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WO2009118218A1 - Dispositif destiné à réduire le bruit de cliquetis dans des boîtes de vitesses à plusieurs rapports - Google Patents

Dispositif destiné à réduire le bruit de cliquetis dans des boîtes de vitesses à plusieurs rapports Download PDF

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Publication number
WO2009118218A1
WO2009118218A1 PCT/EP2009/051532 EP2009051532W WO2009118218A1 WO 2009118218 A1 WO2009118218 A1 WO 2009118218A1 EP 2009051532 W EP2009051532 W EP 2009051532W WO 2009118218 A1 WO2009118218 A1 WO 2009118218A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
main shaft
gears
zei
conical
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.)
Ceased
Application number
PCT/EP2009/051532
Other languages
German (de)
English (en)
Inventor
Friedrich Ehrlinger
Stefan Renner
Jürgen RAUTER
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.)
ZF Friedrichshafen AG
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 WO2009118218A1 publication Critical patent/WO2009118218A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • 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
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F16H2057/128—Arrangements for adjusting or for taking-up backlash not provided for elsewhere using axial positioning of gear wheel with addendum modification on gear width, i.e. backlash is compensated by axial positioning of a slightly conical gear wheel
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H3/095—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts with means for ensuring an even distribution of torque between the countershafts
    • 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
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings

Definitions

  • the present invention relates to a device for reducing rattle noise in multi-stage transmissions with at least two countershafts, according to the preamble of patent claim 1.
  • the main shaft gears are mounted in the radial direction with play on the main shaft to allow load balancing between the power flows through the two countershafts.
  • the main shaft gears which engage in the teeth of the countershaft gears, are radially guided by the teeth of the countershaft gears within their radial range of motion on the main shaft. That is, each mounted on the main shaft movable main shaft centered under load in the teeth of the countershaft gears. This is the case when the associated gear is engaged and engaged and the drive motor operates in push or pull operation. As a result, an optimal load balance between the countershafts is achieved in the torque transmission.
  • the main shaft wheels which are not assigned currently engaged gear stages are in no-load condition.
  • the main shaft wheels In the load-free state, the main shaft wheels float within the backlash, ie they have freedom of movement in the radial direction and in the circumferential direction.
  • the main shaft gears In the axial direction, the main shaft gears are guided for example by thrust washers on the main shaft, wherein the main shaft is disposed between two arranged on the main shaft thrust washers. Due to manufacturing tolerances and required for oil lubrication column, there is also play in the axial direction.
  • the present invention is based on the object of further improving a multi-stage transmission with two countershafts with respect to the reduction of rattle noise. This object is achieved by a device having the features of patent claim 1. Advantageous developments of the device according to the invention are claimed in the dependent claims.
  • the inventive device for reducing rattle noise is provided for a multi-stage transmission with at least one reverse gear and multiple forward gears, which further comprises two countershafts.
  • the power flow is guided via two arranged on the countershafts gears on a centrally disposed on the main shaft gear.
  • the invention is characterized in that at least one gear in at least one gear stage of the multi-speed transmission has a conical toothing that the gear with the conical toothing or a gear meshing with this gear is mounted axially displaceable, and that the gear with the conical toothing and the be meshed with this gear meshing gear by at least one elastic element in the axial direction against each other.
  • the main shaft wheel only the gear wheel arranged centrally on the main shaft, the main shaft wheel, has the conical toothing. It is also axially slidably mounted only the main shaft of the respective gear and the main shaft is pressed by an elastic member in the axial direction in the meshing with him, axially fixed gears.
  • This preferred embodiment takes into account the fact that the arranged on the countershaft gears are advantageously rigidly connected to the associated countershaft in order to ensure a uniform load balance between the two countershafts permanently. Characterized in that in this embodiment, only the main shaft is movably mounted, the countershaft gears can be rigidly mounted on its countershaft or the teeth are made directly and integrally with the countershaft. For the purposes of this patent application gear teeth produced directly on a shaft should also be encompassed by the term gear.
  • both the main shaft wheel and the meshing with him gears have a conical toothing, and that one or all of the said gears are mounted axially displaceable and by an elastic member in the axial direction the respective opposite gear are pressed.
  • the opposite gears each have an opposing conicity.
  • a further preferred embodiment provides that only the reverse gear stage has at least one gear with the conical toothing. Accordingly, all the gears of the forward gear stages are provided with a conventional, non-conical toothing.
  • the rattle noise in all grades are significantly reduced by this measure. This is due to the fact that the rattle noise in all gears is mainly caused by vibrations in the reverse gear.
  • the rattle noise of the entire multistage transmission is reduced, i. even with a relatively large backlash having, not running under load forward gear steps are much less likely to rattle.
  • a significant reduction of the annoying rattling noises of the entire transmission can be achieved inexpensively with little design effort. It is therefore not necessary to reduce the backlash in all gear stages of a multi-stage gearbox in order to achieve the desired noise reduction target.
  • the advantage of the measures used to reduce the rattle noise only in the reverse gear is also very large, because a vehicle transmission is mainly operated in one of the forward gears, while the reverse gear runs along with no load and causes rattle noise in a conventional transmission. Especially in these periods of predominant operating phases, the advantages of the present invention come to fruition.
  • the main shaft and the intermediate gears of the reverse gear stage have a conical shape, that the mutually engaged gears each have an opposing conicity, and that the main shaft or the intermediate wheels of the reverse gear are axially displaceable and each having an elastic Element are pressed in the axial direction in the opposite teeth.
  • all the gears of the reverse gear stage may have a conical shape, wherein the meshing gears each having an opposing conicity, and wherein at least one of the gears in each gear chain of the reverse gear is axially displaceable and from an elastic member in the axial direction in the opposite Toothing is pressed.
  • Said elastic element is preferably a disc spring. Also other elastic elements, such as e.g. Rubber rings are used.
  • the invention is suitable for multi-speed transmission both with straight-toothed, and with helical gears.
  • Spur-toothed gears are simple and inexpensive to manufacture and cause in operation no axial forces that need to be compensated by other design measures.
  • Helical gears ensure quiet, noisy poor running and thus an even longer life of the components of the entire drive train.
  • the conical toothing on the respective gears is preferably designed as Beveloidverschwung.
  • the life of the components of the entire drive train because the gears of all non-lying in the power flow grades no longer beat so strong and so often against each other. This also results in a smoother running of the entire drive train.
  • FIG. 1 shows a detail of a multi-speed transmission with a first embodiment according to the invention of a gear stage for the reverse gear in a schematic representation.
  • Fig. 2 shows a detail of a multi-speed transmission with a second embodiment according to the invention a gear stage for the reverse gear in a schematic representation
  • Fig. 3 shows a detail of a multi-speed transmission with a third embodiment of a gear stage according to the invention for the reverse gear in a schematic representation.
  • Fig. 1 shows an embodiment of the invention in the gear stage for reverse.
  • the torque to be transmitted is guided by the two countershafts 10 and 20 via the intermediate wheels 31 and 41 on the main shaft 1 rotatably mounted on a central main shaft 3 about the central axis 2 thereof. Of the main shaft 3, only a portion is shown, which is cut off at both ends.
  • the central main shaft 1 is mounted on the main shaft 3 with radial clearance 7, to allow a uniform load balance between the two countershafts 10 and 20. It has an outer contour with non-conical shape.
  • the main shaft 1 is guided by at least one arranged on the main shaft thrust washer 4 in the axial direction.
  • Each of the countershafts 10 and 20 rotates about their respective central axis 12 and 22. Shown is only one end portion of the countershafts 10 and 20. The end portion of each countershaft 10 and 20 carries a toothing 1 1 and 21. In this embodiment, the teeth 1 1 and 21 executed directly on the respective countershaft 10, 20. However, it is also possible in each case to arrange a prefabricated gear rotatably on the countershafts 10 and 20. The outer contours of the teeth 1 1 and 21 on the countershafts 10, 20 have a non-conical shape in this embodiment.
  • the two intermediate wheels 31 and 41 are each rotatable on an intermediate wheel axle 33 and 43 about their respective center axes 32 and 42 and have a conical toothing.
  • the insectsen 33 and 43 are fixed or fixed to the housing in each case two bearings 34, 35 and 44, 45.
  • the intermediate wheels 31 and 41 are mounted axially movably on their associated intermediate wheel axle 33, 43.
  • the intermediate wheels 31 and 41 for this purpose on the respective Eisenradach- se 33, 43 by means of bearings 36, 46 are mounted.
  • the bearings 36, 46 can, for example, be executed as a needle bearing.
  • the axial movement of the intermediate wheels 31, 41 on the insectsen 33, 43 is limited in both directions by the bearings 34, 35 and 44, 45, unless he is already restricted by the conical toothing of the idler gears 31, 41.
  • each insects 33, 34 further comprises a plate spring 37, 47 is arranged, which presses the associated intermediate 31, 41 via an annular disc 38, 48 in the axial direction in the respective counter teeth of the main shaft 1 and the countershaft 10, 20.
  • the disc springs 37, 47 and the annular discs 38, 48 are respectively disposed between the intermediate 31 and 41 and the bearing 35 and 45 and are based on the intermediate wheel 31, 41 facing away from the associated bearing 35, 45 from.
  • the taper of the intermediate wheels 31, 41 is directed so that the outer diameter decreases in the effective direction of the plate spring 37, 47.
  • the conical intermediate wheels 31, 41 of the associated disc spring 37, 38 always pushed so far into the meshing with the intermediate gears teeth of the main shaft 1 and the countershafts 10, 20 that the tooth flanks of the intermeshing teeth abut each other and a backlash avoided becomes.
  • a quieter running of the transmission is achieved and annoying rattling noises are avoided or at least significantly reduced.
  • FIG. 2 corresponds to a large extent to the embodiment of Fig. 1. Therefore, the same parts in the figures with the same reference numerals. To describe the same parts and their function, reference is made to the description of FIG.
  • the main shaft 1 is supported in the axial direction against the force exerted by the disc springs 37, 47 pressure on a thrust washer 4 from.
  • Fig. 3 corresponds to a large extent to the embodiment of Fig. 1. Therefore, the same parts in Fig. 3 are provided with the same reference numerals as in Fig. 1. For description of the same parts and their function will be to the description of Fig. 1 referenced.
  • the elastic element for pressing against each other of the intermeshing teeth is assigned to the main shaft 1 here.
  • a plate spring 5 which is arranged on the main shaft 3 between an annular disc 6 and the main shaft 1.
  • the plate spring 5 is supported in the axial direction via the annular disc 6 on the thrust washer 4 against the main shaft 1 from.
  • the intermediate wheels 31 and 41 are axially non-displaceably mounted on the Eisenradachsen 33 and 43 in the embodiment of FIG.
  • the intermediate wheels 31 and 41 are on the Eisenradachsen 33rd and 43 between each thrust washer 39, 49 and an annular disc 38, 48 and are held by them axially in position, wherein the annular disc 38, 48 in the axial direction of the adjacent bearing 35, 45 is supported.

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

Abstract

L'invention concerne un dispositif destiné à réduire le bruit de cliquetis dans une boîte de vitesses à plusieurs rapports présentant au moins une marche arrière et plusieurs marches avant, dispositif comprenant au moins deux arbres intermédiaires (10, 20). Le flux de force est dirigé, via des engrenages (11, 21) montés sur les arbres intermédiaires (10, 20), vers un engrenage central (1) monté sur un arbre principal (3). L'invention est caractérisée en ce qu'au moins un engrenage (1, 11, 21, 31, 41) présente une denture conique dans au moins un rapport de la boîte de vitesses à plusieurs rapports. L'engrenage (1, 11, 21, 31, 41) présentant l'engrenage conique, ou un engrenage (1, 11, 21, 31, 41) en prise avec cet engrenage, est en outre monté déplaçable axialement et est précontrant axialement, par un élément élastique (5, 37, 47), de telle façon que les dentures viennent mutuellement en prise en étant pressées les unes contre les autres.
PCT/EP2009/051532 2008-03-26 2009-02-11 Dispositif destiné à réduire le bruit de cliquetis dans des boîtes de vitesses à plusieurs rapports Ceased WO2009118218A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810000820 DE102008000820A1 (de) 2008-03-26 2008-03-26 Einrichtung zur Reduzierung von Rasselgeräuschen in Mehrstufenschaltgetrieben
DE102008000820.6 2008-03-26

Publications (1)

Publication Number Publication Date
WO2009118218A1 true WO2009118218A1 (fr) 2009-10-01

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/051532 Ceased WO2009118218A1 (fr) 2008-03-26 2009-02-11 Dispositif destiné à réduire le bruit de cliquetis dans des boîtes de vitesses à plusieurs rapports

Country Status (2)

Country Link
DE (1) DE102008000820A1 (fr)
WO (1) WO2009118218A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014223472A1 (de) * 2014-11-18 2016-05-19 Zf Friedrichshafen Ag Schwenkmotorgetriebe für ein Wankstabilisierungssystem
CN114087281A (zh) * 2021-12-09 2022-02-25 中国船舶重工集团公司第七0三研究所 单斜齿锥面弹性减振止推环及带有该止推环的齿轮传动结构
CN115419698A (zh) * 2021-06-11 2022-12-02 福建省真发齿轮股份有限公司 降冲击齿轮
US20240039458A1 (en) * 2020-08-28 2024-02-01 Jeong Hoon SHIN Solar photovoltaic rotation device having backlash control structure

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008002294A1 (de) 2008-06-09 2009-12-10 Zf Friedrichshafen Ag Anordnung zur Rasselreduzierung bei einem Getriebe
DE102009046857A1 (de) * 2009-11-19 2011-05-26 Zf Friedrichshafen Ag Stellgetriebe und Verwendung des Stellgetriebes
DE102010043599A1 (de) * 2010-11-09 2012-05-10 Zf Friedrichshafen Ag Lageranordnung für eine Welle und Verfahren zum axialen Fixieren der Lageranordnung
DE102011017230A1 (de) * 2011-04-15 2012-08-16 Daimler Ag Stelleinrichtung zum variablen Einstellen eines Verdichtungsverhältnisses einer Verbrennungskraftmaschine
US10336217B2 (en) 2014-04-07 2019-07-02 Delta Kogyo Co., Ltd. Seat lifter and gear mechanism
DE102019120260A1 (de) * 2019-07-26 2021-01-28 Schaeffler Technologies AG & Co. KG Zahnradanordnung mit einem Axialfedermittel
CN111536205B (zh) * 2020-05-21 2021-06-01 安徽津野数控科技有限公司 一种数控机床用低回程间隙行星减速器

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0084197A1 (fr) * 1982-01-18 1983-07-27 Mavilor Systèmes S.A. Transmission avec engrenages à mouvement orbital
EP0321119A1 (fr) * 1987-12-14 1989-06-21 Borg-Warner Automotive, Inc. Mécanisme d'élimination de bruit d'engrenage dans des transmissions à rapport de vitesse variable
EP0572126A1 (fr) * 1992-05-28 1993-12-01 Eaton Corporation Combinaison de rondelles de butée pour un arbre principal d'une boîte de vitesses
DE19712516A1 (de) * 1997-03-25 1998-10-01 C H Schaefer Getriebe Gmbh Planetengetriebe
DE10306935A1 (de) * 2003-02-19 2004-09-02 Zf Friedrichshafen Ag Zahnradgetriebe
DE102004057126A1 (de) * 2004-11-26 2006-06-08 Zf Friedrichshafen Ag Einrichtung zur Reduzierung der Axialbewegung der Hauptwellenräder bei einem Getriebe mit zumindest zwei Vorgelegewellen

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0084197A1 (fr) * 1982-01-18 1983-07-27 Mavilor Systèmes S.A. Transmission avec engrenages à mouvement orbital
EP0321119A1 (fr) * 1987-12-14 1989-06-21 Borg-Warner Automotive, Inc. Mécanisme d'élimination de bruit d'engrenage dans des transmissions à rapport de vitesse variable
EP0572126A1 (fr) * 1992-05-28 1993-12-01 Eaton Corporation Combinaison de rondelles de butée pour un arbre principal d'une boîte de vitesses
DE19712516A1 (de) * 1997-03-25 1998-10-01 C H Schaefer Getriebe Gmbh Planetengetriebe
DE10306935A1 (de) * 2003-02-19 2004-09-02 Zf Friedrichshafen Ag Zahnradgetriebe
DE102004057126A1 (de) * 2004-11-26 2006-06-08 Zf Friedrichshafen Ag Einrichtung zur Reduzierung der Axialbewegung der Hauptwellenräder bei einem Getriebe mit zumindest zwei Vorgelegewellen

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014223472A1 (de) * 2014-11-18 2016-05-19 Zf Friedrichshafen Ag Schwenkmotorgetriebe für ein Wankstabilisierungssystem
DE102014223472B4 (de) 2014-11-18 2018-11-29 Zf Friedrichshafen Ag Schwenkmotorgetriebe für ein Wankstabilisierungssystem
US20240039458A1 (en) * 2020-08-28 2024-02-01 Jeong Hoon SHIN Solar photovoltaic rotation device having backlash control structure
US12113475B2 (en) * 2020-08-28 2024-10-08 Jeong Hoon SHIN Solar photovoltaic rotation device having backlash control structure
CN115419698A (zh) * 2021-06-11 2022-12-02 福建省真发齿轮股份有限公司 降冲击齿轮
CN114087281A (zh) * 2021-12-09 2022-02-25 中国船舶重工集团公司第七0三研究所 单斜齿锥面弹性减振止推环及带有该止推环的齿轮传动结构

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