WO2015158554A1 - Boîte de vitesse manuelle - Google Patents

Boîte de vitesse manuelle Download PDF

Info

Publication number
WO2015158554A1
WO2015158554A1 PCT/EP2015/057280 EP2015057280W WO2015158554A1 WO 2015158554 A1 WO2015158554 A1 WO 2015158554A1 EP 2015057280 W EP2015057280 W EP 2015057280W WO 2015158554 A1 WO2015158554 A1 WO 2015158554A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
countershaft
gears
idler
manual transmission
Prior art date
Application number
PCT/EP2015/057280
Other languages
German (de)
English (en)
Inventor
Thomas Schleich
Andreas Pfeffer
Original Assignee
Bayerische Motoren Werke Aktiengesellschaft
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 Bayerische Motoren Werke Aktiengesellschaft filed Critical Bayerische Motoren Werke Aktiengesellschaft
Publication of WO2015158554A1 publication Critical patent/WO2015158554A1/fr

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
    • 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
    • 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
    • F16H2003/0822—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 arrangement of at least one reverse gear
    • 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
    • F16H2003/0826—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 wherein at least one gear on the input shaft, or on a countershaft is used for two different forward gear ratios
    • 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
    • F16H2003/0931—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 each countershaft having an output gear meshing with a single common gear on the output shaft
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds

Definitions

  • the invention relates to a manual transmission.
  • this is achieved in a manual transmission with a transmission input shaft, on which at least three fixed wheels are arranged, and a first and a second countershaft, on each of which at least three idler gears are arranged, each associated with a switching element, all three fixed gears, each with a Idler gear of the first countershaft and a loose wheel of the second countershaft are engaged and can be rotatably connected via the switching elements either one of the two idler gears with the respective countershaft.
  • each of the three fixed gears of the transmission input shaft can be used in a dual function for two gears. This reduces the number of fixed wheels required, which results in an increase in space in the axial direction.
  • the space created in this way can be used, for example, for coaxially arranged electric motors in hybrid applications and / or create additional installation space for damping systems.
  • the three fixed wheels preferably define two forward gears each.
  • Four fixed wheels are preferably arranged on the transmission input shaft, and four loose wheels are provided on each of the countershafts. With this arrangement, a seven-speed gearbox with reverse gear can be realized.
  • one of the idler gears on the second countershaft is associated with a reverse gear.
  • the reverse gear associated idler gear can be coupled to a loose wheel of the first countershaft.
  • the second countershaft serves as an output shaft for the reverse gear.
  • the fixed gear used to drive the reverse gear and the idler gear used to reverse the direction of rotation of the first countershaft are associated with a first gear of the manual transmission.
  • all four fixed wheels are used twice. About seven of the idler gears in each case a forward gear is driven, while on the eighth idler gear in conjunction with a loose wheel of the first countershaft reverse gear is switched.
  • one of the idler gears on the second idle shaft is coupled to an intermediate gear of a reverse gear, and the idler gear may be coupled to one of the fixed gears.
  • the direction reversal required for the reverse gear is achieved by the intermediate gear.
  • the idler gear is preferably in constant mesh with the idler gear defining the reverse gear.
  • the fixed wheel is preferably associated with the first gear of the manual transmission corresponding loose wheel on the first countershaft.
  • each of the fixed gears on the transmission input shaft is used twice.
  • two adjacent switching elements can be combined to form a switching unit, which can be moved along the respective countershaft in both axial directions to rotatably couple the idler gears with the respective countershaft.
  • the assignment of the fixed wheels to the loose wheels on the respective countershafts is fixed in the described embodiments.
  • the fixed wheels are preferably in constant engagement with the respective loose wheels.
  • FIG. 1 is a schematic representation of a manual transmission according to the invention in a first embodiment
  • FIG. 2 shows a switching matrix of the manual transmission from FIG. 1;
  • Figure 3 is a diagrammatic representation of the translation of the manual transmission of Figure 1;
  • FIG. 4 shows an inventive manual transmission according to a second embodiment
  • Figure 5 is a switching matrix of the manual transmission of Figure 4.
  • FIG. 6 shows a diagrammatic illustration of the transmission of the manual transmission from FIG. 4.
  • Figure 1 shows a manual transmission 10 in a first embodiment, wherein the manual transmission 10 is provided in this example for a front-transverse installation.
  • the manual transmission 10 is designed as a three-shaft transmission, with a transmission input shaft 12 and a first countershaft 14 and a second countershaft 16. Each of the two countershafts 14, 16 is rotatably connected in known manner with an output shaft 18.
  • a switching unit 24 is arranged in each case, which in each case combines two switching elements (denoted by A to D in the figures).
  • a to D switching elements
  • a switching unit 24 is disposed between the idler gears 28a and 28b and between the idler gears 28c and 28d, each switching unit 24 has two switching elements E - H for the rotationally fixed connection of the respective idler gear 28a to 28d with the second countershaft 16 summarized.
  • the loose wheels 28a, 28b and 28c on the second countershaft 16 mesh with the fixed wheels 20a, 20b and 20c on the transmission input shaft 12 in constant engagement.
  • the idler gear 28d on the second countershaft 16 is associated with a reverse gear R, while the remaining idler gears 22a-d, 28a-c are each associated with a forward gear.
  • the manual transmission 10 therefore has seven forward gears 1-7 and one reverse R.
  • the associated shift unit 24 is moved in the direction of the associated idler gear 22a-d, 28a-c, so that the gear wheel directed to the idler gear A - G comes into engagement with the idler gear and this rotatably with the respective countershaft 14, 16 connects. Since the countershafts 14, 16 are rotatably coupled to the output shaft 18, the power flow from the engine through the transmission input shaft 12, the respective idler gear 22 a -d, 28 a-c and the respective countershaft 14, 16 is transmitted to the output shaft 18.
  • the second idler gear on the respective other countershaft 14, 16 remains in engagement with the respective fixed gear 20a-c and runs freely even when engaged gear.
  • Each of the fixed wheels 20a, 20b and 20c undergoes a double use in the manual transmission 10 for a respective gear, which is arranged on the first countershaft 14, and in each case one gear, which is arranged on the countershaft 16.
  • the switching element H When engaging the reverse gear R, the switching element H is brought into engagement with the idler gear 28d, so that the idler gear 28d is rotatably connected to the second output shaft 16.
  • the idler gear 28d is engaged with the idler gear 22d meshing with the fixed gear 20d on the first countershaft 14, so that the idler gear 22d functions as an idler gear and causes a reversal of the direction of rotation.
  • the idler gear 22d is not coupled to the first countershaft 14, but runs loose on this. In this way, the power flow through the transmission input shaft 12, the fixed gear 20 d, the idler gear 22 d and the idler gear 28 d is transmitted to the second countershaft 16 and from there with the reverse direction as in the forward gears 1 to 7 on the output shaft 18.
  • the fixed gear 20d and the idler gear 22d are here associated with the first gear of the manual transmission 10.
  • Each of the fixed gears 20a to 20d on the transmission input shaft is used twice here.
  • the three fixed wheels 20a, 20b, 20c are each simultaneously with two idler gears 22a-c, 28a-c of the two countershafts 14, 16 in engagement while the fixed gear 20d in constant engagement with the idler gear 22d on the first countershaft 14 and on the Coupling of the loose wheel 28d on the second countershaft 16 with the idler gear 22d of the first countershaft 14 also the reverse gear R operated.
  • the grading of the manual transmission 10 is shown in Figure 3, wherein the dashed line indicates the ratio realized by the manual transmission 10, while the solid line describes the ideal desired state. As can be seen, the manual transmission 10 forms the ideal course very well. With the manual transmission 10, a high overall transmission spread of> 7.5 can be achieved.
  • the diameters of the individual fixed wheels 20a-d and the loose wheels 22a-d, 28a-d are determined by the desired transmission ratio of the manual transmission 10 and the geometric specifications by the arrangement of the transmission input shaft 2 and the two countershafts 14, 16th
  • FIG. 1 A possible switching matrix for the manual transmission 10 is shown in FIG. There, the respective switching elements A to H are the individual Assigned gears (forward gears 1 to 7 and reverse gear R), wherein the switching elements A to H are each assigned to the adjacent idler gear 22a-d and 28a-d shown in Figure 1.
  • FIGS. 4 to 6 show a second embodiment of a manual transmission 100.
  • a transmission input shaft 12 is provided on the four fixed wheels 120a-d are arranged rotationally fixed.
  • Each of the fixed gears 120b, 120c and 120d constantly meshes with two idler gears, with the fixed gear 120b in engagement with the idler gears 122b and 128b, the fixed gear 120c with the idler gears 122c and 128c and the fixed gear 122d with the idler gears 122d and 128d.
  • switching units 24 each having two switching elements A-H are arranged between each of the idler gears for rotationally fixed connection of a respective idler gear 122a-d, 128a-d to the respective countershaft 14, 16.
  • the associated shift unit 24 is moved in the direction of the adjacent idler gear 122a-d, 128b-d, so that the respective shift element A - D, F - H in engagement with the respective idler gear 122a -d, 128b-d comes and rotatably connected to the respective countershaft 14, 16 connects.
  • the other idler wheel which meshes with the fixed gear 120b-d, moves freely with it.
  • an intermediate wheel 130 is provided which constantly meshes with the idler gear 128a on the second countershaft 16. To engage the reverse gear R, this intermediate gear 130 is brought into engagement with the fixed gear 120a on the transmission input shaft 12, so that a power transmission from the transmission input shaft 12 via the intermediate gear 130 to the idler gear 128a takes place.
  • the idler gear 28a is rotatably connected by the switching element E with the second countershaft 16. Through the intermediate intermediate wheel 130 there is a reversal of rotation, so that the output shaft 18 is rotated in the reverse direction than in the forward gears 1 to 7.
  • the fixed gear 120a is assigned here to the first gear.
  • each of the fixed gears 120a-d on the transmission input shaft 12 performs a dual function and operates two gears each.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne une boîte de vitesse manuelle comportant un arbre d'entrée (12), sur lequel sont disposés trois roues fixes (20a-d ; 120a-d) ou plus, et des premier et second arbres de renvoi (14, 16) sur chacun desquels sont disposées trois roues libres (22a-d, 28a-d ; 122a-d, 128a-d) ou plus à chacune desquelles est associé un élément de commutation (A-H). Les trois roues fixes (20a-d ; 120a-d) ou plus sont chacune en engagement avec une roue libre (22a-d ; 122a-d) du premier arbre intermédiaire (14) et une roue libre (28a-d ; 128a-d) du second arbre intermédiaire (16) et les éléments de commutation (AH) au choix de l'une des deux roues libres (22a-d, 28a-d ; 122a-d, 128a-d) peuvent être reliés de manière solidaire en rotation à l'arbre intermédiaire (14, 16) respectif. Un mode de réalisation de la boîte de vitesses manuelle comporte quatre roues fixes, sept rapports de marche avant et un rapport de marche arrière (voir figure 1), les quatre roues fixes ayant une double utilisation. L'encombrement requis dans la direction axiale est réduit. On obtient en même temps une gradation de vitesse ciblée presque idéale sur un plage globale élevée.
PCT/EP2015/057280 2014-04-16 2015-04-02 Boîte de vitesse manuelle WO2015158554A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014207286.7A DE102014207286A1 (de) 2014-04-16 2014-04-16 Handschaltgetriebe
DE102014207286.7 2014-04-16

Publications (1)

Publication Number Publication Date
WO2015158554A1 true WO2015158554A1 (fr) 2015-10-22

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/057280 WO2015158554A1 (fr) 2014-04-16 2015-04-02 Boîte de vitesse manuelle

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Country Link
DE (1) DE102014207286A1 (fr)
WO (1) WO2015158554A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016115185B3 (de) * 2016-08-16 2017-09-14 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Manuell schaltbares Getriebe in Vorgelegebauweise
DE102016115179A1 (de) 2016-08-16 2018-02-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Manuell schaltbares Getriebe in Vorgelegebauweise

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201600122071A1 (it) * 2016-12-01 2018-06-01 Piaggio & C Spa Trasmissione sincrona a elevato rendimento

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2815103A1 (fr) * 2000-10-10 2002-04-12 Peugeot Citroen Automobiles Sa Dispositif de commande de boite de vitesses a cremaillieres opposees, et application
WO2003019043A1 (fr) * 2001-08-22 2003-03-06 Zf Friedrichshafen Ag Transmission a deux arbres de renvoi
GB2478298A (en) * 2010-03-02 2011-09-07 Gm Global Tech Operations Inc Manual transmission for vehicle with overdrive

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10305242A1 (de) * 2003-02-08 2004-09-23 Zf Friedrichshafen Ag Sechs- oder siebengängiges Schaltgetriebe für ein Kraftfahrzeug
JP2013213568A (ja) * 2012-04-04 2013-10-17 Aisin Ai Co Ltd 車両用手動変速機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2815103A1 (fr) * 2000-10-10 2002-04-12 Peugeot Citroen Automobiles Sa Dispositif de commande de boite de vitesses a cremaillieres opposees, et application
WO2003019043A1 (fr) * 2001-08-22 2003-03-06 Zf Friedrichshafen Ag Transmission a deux arbres de renvoi
GB2478298A (en) * 2010-03-02 2011-09-07 Gm Global Tech Operations Inc Manual transmission for vehicle with overdrive

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016115185B3 (de) * 2016-08-16 2017-09-14 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Manuell schaltbares Getriebe in Vorgelegebauweise
DE102016115179A1 (de) 2016-08-16 2018-02-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Manuell schaltbares Getriebe in Vorgelegebauweise
DE102016115179B4 (de) * 2016-08-16 2018-03-01 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Manuell schaltbares Getriebe in Vorgelegebauweise

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Publication number Publication date
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