WO2015113660A1 - Boîte de vitesses à au moins huit vitesses avant - Google Patents

Boîte de vitesses à au moins huit vitesses avant Download PDF

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Publication number
WO2015113660A1
WO2015113660A1 PCT/EP2014/073819 EP2014073819W WO2015113660A1 WO 2015113660 A1 WO2015113660 A1 WO 2015113660A1 EP 2014073819 W EP2014073819 W EP 2014073819W WO 2015113660 A1 WO2015113660 A1 WO 2015113660A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
shaft
gears
idler
countershaft
Prior art date
Application number
PCT/EP2014/073819
Other languages
German (de)
English (en)
Inventor
Thomas Gumpoldsberger
Thomas LUGMAYR
Original Assignee
Magna Powertrain Ag & Co 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
Publication date
Application filed by Magna Powertrain Ag & Co Kg filed Critical Magna Powertrain Ag & Co Kg
Priority to DE112014006297.9T priority Critical patent/DE112014006297A5/de
Publication of WO2015113660A1 publication Critical patent/WO2015113660A1/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
    • F16H3/091—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 including a single countershaft
    • F16H3/0915—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 including a single countershaft with coaxial input and output shafts
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0013—Transmissions for multiple ratios specially adapted for rear-wheel-driven vehicles
    • 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
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
    • 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
    • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
    • 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
    • F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
    • 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
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds

Definitions

  • the present invention relates to a change gear for the realization of at least eight gears, which can be performed both as a pure manual transmission and as an automated manual transmission.
  • Such change gear can be configured as a spur gear with an input and an output shaft and a parallel countershaft, by means of which the torque is transmitted from the input shaft to the output shaft.
  • a plurality of gears designed as idler gears (ie, rotatably mounted gears), which mesh with associated fixed wheels on the countershaft (ie fixedly connected to the countershaft gears).
  • the individual idler gears are formed differently large and can be connected by means of shift sleeves with the input shaft rotation, so that by each gear pair of intermeshing gears on the input and the countershaft another gear ratio is displayed.
  • the transmission according to the invention has inter alia a first shaft, a second shaft, which is aligned axially with the first shaft, and a parallel to these two shafts countershaft.
  • first shaft which may preferably be a transmission input shaft
  • second shaft which may preferably be a transmission output shaft.
  • the transmission according to the invention has a gear designated here as the fifth idler gear which is rotatable relative to the first and second shafts and which is aligned coaxially with the first to fourth gears.
  • the countershaft has at least five counter-gears, each of which directly or indirectly meshes with another of the five gears axially aligned with the first and second shafts are, whereby a first, a second, a third, a fourth and a fifth gear pair are formed.
  • the drive furthermore has a first, a second, a third and a fourth shifting device, one of the gears of the first to fourth gear pairs being a fixed gear (ie a toothed wheel permanently connected to the associated shaft or counter gear) and the other gear of the respective gear pair is a loose wheel (ie, a rotatably mounted on the associated shaft gear or counter gear), which is non-rotatably connected by means of the respective switching device with the shaft on which it is arranged.
  • a fixed gear ie a toothed wheel permanently connected to the associated shaft or counter gear
  • loose wheel ie, a rotatably mounted on the associated shaft gear or counter gear
  • the fifth idler gear is arranged axially between the first and the second shaft and optionally with the first shaft, or with the second shaft, or with the first and the second shaft by means of a fifth and / or. or a sixth switching device can be rotatably connected.
  • the eight-speed change gear according to the invention thus has only five tracks, which are formed by the mutually directly or indirectly intermeshing pairs of idler gears and fixed wheels, so that the transmission requires only relatively little space in the axial direction .
  • the fact that the transmission according to the invention makes do with only five tracks for the realization of eight gears is due to the fact that the change gear according to the invention basically consists of a main gear and an auxiliary gear or an additional gear stage upstream or downstream thereof.
  • the main gear is formed, inter alia, by the three tracks of the first wave, whereas the additional gear is formed inter alia by the track of the second shaft.
  • the fifth gear (idler gear between the first shaft and the second shaft) is not required for torque transmission between the countershaft and the second shaft ,
  • the fifth gear can therefore be selectively connected in a rotationally fixed manner to the first shaft, whereby a fourth gear can be switched in addition to the three gears of the first three tracks, which means that in this case the fifth gear becomes part of the main gear.
  • the fifth gear can optionally be rotatably connected to the second shaft, so that the torque transmission between the second shaft and the countershaft is no longer on the fourth gear and the thus meshing counter-gear, but can be done via the fifth gear.
  • four further gears are connected, in which the torque transmission between the second shaft and the countershaft is over the fifth gear, which means that in this case the fifth gear becomes part of the additional gear.
  • the fifth gear according to the invention so to speak, assigned a dual function by this on the one hand in the case of a rotationally fixed connection with the first shaft as a gear wheel, and on the other hand in the case of a rotationally fixed connection with the second shaft for the realization of a second transmission ratio range, for example, a "High Range ", in which the gear ratios of the main gear are additionally subjected to a different translation than via the fourth gear on the second shaft.
  • a change gear with a main gear and an upstream or downstream auxiliary gear available, with the individual ratios of the main transmission different transmission ratios can be subjected, with the main gear and the additional gear a common idler gear (said fifth gear ) "share".
  • the fifth gear is not required for torque transmission between the countershaft and the second shaft, the fifth gear in the manner according to the invention can be used as a gear for the main gear, so that compared to a gear assembly with a completely separate additional gear one less track is needed to provide the same number of gears.
  • the respective gear and the associated counter gear can mesh directly with each other.
  • the respective gear and the associated counter gear are only indirectly connected in a rotationally effective manner, namely meshing with one another only via an intermediate gear.
  • a reversal of rotation can be realized in order to realize this pair of gears or this track two reverse gears (two gears the same direction of rotation due to the explained effect of the additional gear).
  • the fifth gear (idler gear) is preferably rotatably supported both with respect to the first and with respect to the second shaft. Although it would be possible to rotatably support the fifth gear on a dedicated bearing between the two shafts. According to a preferred embodiment, however, it is provided to support the fifth gear rotatably on both the first and on the second shaft, since this no additional weight for corresponding bearing components for the fifth gear is obtained.
  • the first and the second gear are each a loose on the first shaft rotatably mounted idler gear, whereas the first and second counter gear is in each case a non-rotatably connected to the countershaft Festrad, and wherein the first and second switching means is associated with the first and the second gear.
  • the first and the second gearwheel may each be a fixed wheel rotatably connected to the first shaft, wherein the first and second counter gearwheel is in each case a loose wheel mounted rotatably on the countershaft, and wherein the first and second shifting device corresponds to the first or second shifting device is associated with the second counter gear.
  • the third gear is rotatably mounted on the first shaft idler gear and the fourth gear is rotatably mounted on the second shaft idler gear, wherein the third and fourth counter gear each having a rotatably connected to the countershaft fixed gear, and wherein the third and fourth switching means are associated with the third and the fourth gear.
  • the third switching device for rotationally fixed connection of the third gear to the first shaft is preferably adjacent to the fifth switching device, so that the third and fifth switching device can be formed by a common switching means such as a two-way shift sleeve.
  • the fourth and sixth switching means may be formed by a common switching means such as a two-way shift sleeve, when the fourth switching means for rotationally fixed connection of the fourth gear to the second shaft is adjacent to the sixth switching means.
  • the first and the second switching device, the third and the fifth switching device, and the fourth and the sixth switching device connected in pairs are and comprise a common respective switching means, which is formed for example by a two-way shift sleeve, which can be brought in a conventional manner by synchronizing rings after the speed synchronization with the associated idler gear engaged or engaged to a rotationally fixed connection between the respective idler gear and the associated shaft.
  • the change gear according to the invention has a control device which is adapted to realize the at least eight gears to engage either the fourth or the sixth switching device and at the same time one of the first, second, third and fifth switching devices. Since only the fourth or the sixth shifting device is always engaged during the two transmission ranges, which can be realized by selectively connecting the fourth and the fifth gear (designed as a loose wheel) to the respective shaft, it is therefore necessary to change gear between two successive gears Gangs only the operation of two of the other switching devices, such as the disengagement of the third switching device and the engagement of the first switching device to switch from the first to second gear, which in particular in the case of the formation of the change gear according to the invention as a manual transmission only the axial displacement of a single shift sleeve requirement.
  • At least one further gear is arranged in addition to the three gears, which at least indirectly (ie directly combing or via another gear) with at least one other counterpart Gear of the countershaft is rotationally connected.
  • a ninth and tenth forward gear or two reverse gears can be realized, which means that the transmission for the realization of, for example, a total of ten gears in total only six tracks needed.
  • the fifth gear (idler gear) in the manner according to the invention has a double function in that it can be connected in a rotationally fixed manner optionally to the first shaft or to the second shaft or simultaneously to both the first and the second shaft.
  • Fig. 1 shows a schematic representation of a part of a vehicle which is designed with the change gear according to the invention
  • Fig. 2 shows schematically the power transmission paths in the gears 1 to 4 of the transmission according to the invention and a shift table
  • Fig. 3 shows schematically the power transmission paths in the gears 5 to 8 of the change gear according to the invention and again the switching table already shown in FIG. 2.
  • FIG. Fig. 1 shows the rear part of a vehicle 100 with rear-wheel drive.
  • the vehicle 100 and its rear wheels 124 are driven by an engine 16, such as an internal combustion engine.
  • the torque of the engine 1 16 is transmitted via a flywheel 1 18 and a clutch 120 and the inventive transmission 1 10 to an axle differential 126 which divides the torque for transmission to the two rear wheels 124 on the two half-shafts 122 of the rear axle.
  • the transmission 1 10 has a transmission input shaft 40 and a transmission output shaft 50, which are rotatably mounted in the gear housing 128 of the transmission 1 10 and extending out of this.
  • a countershaft 60 is rotatably mounted within the gear housing 128, via which the torque is transmitted from the input shaft 40 indirectly to the output shaft 50.
  • three differently sized idler gears are rotatably mounted in the illustrated embodiment, namely the idler gears 1 1, 12, 13.
  • the idler gears 1 1, 12, 13 are gear wheels designed as gears for the realization of a second, fourth or first gear, as is indicated in Fig. 1 by the corresponding numerals.
  • a fourth idler gear 14 is rotatably mounted on the transmission output shaft 50 and serves to realize a lower gear transmission range, as is indicated in Fig. 1 by the abbreviation "Lo".
  • the relatively largest fourth idler gear 14 (high gear to slow) is the along the torque transmission path to the transmission output nearest gear, so that located between the engine 1 16 and the fourth gear 14 transmission components have to transmit relatively little torque, especially in the lower gear ratio range and Consequently, they can be dimensioned less strongly.
  • a fifth idler gear 15 is coaxially aligned with the four idler gears 1 1, 12, 13, 14, wherein the fifth idler gear 15 is located between the input shaft 40 and the output shaft 50 and is preferably rotatably mounted on these shafts 40, 50.
  • With the countershaft 60 five fixed wheels 21, 22, 23, 24, 25 are rotatably connected, wherein each of these fixed wheels with an associated one of the idler gears 1 1, 12, 13, 14, 15 meshes and thus forms a respective counter-gear.
  • the change gear 1 10 has a total of five tracks, each of which is defined by a pair of intermeshing loose or fixed wheels (ie gears and counter-gears).
  • serving as a gear wheel second idler gear 12 for the fourth gear is immediately adjacent to serving as a gear idler gear 1 1 for the second arranged.
  • This arrangement is particularly suitable for an automated manual transmission, whereas in the case of a pure manual transmission, in contrast to the illustrated embodiment, the positions of the gear wheels 12, 13 should be interchanged for the fourth or first gear to the transmission via a H- Switching circuit or an H-shaped shift gate can.
  • the first and second speed gears and third and fourth speed gears are respectively shifted by means of a two-way shift sleeve disposed between the respective gear wheels, so that, for example, the shift sleeve associated with the first two gears disengages with the first Gear wheel can be decoupled and can be brought into engagement with the second gear wheel when the gearshift lever is moved in the shift gate from the first gear alley via the neutral position into the second-speed lane.
  • each of the five loose wheels 1 1, 12, 13, 14, 15 at least one switching device 31, 32, 33, 34, 35, 36 associated to the idler gears 1 1, 12, 13, 14, 15 to connect with the respective shaft 40, 50 rotatably.
  • a switching device 35, 36 is assigned to the fifth idler gear 15 either to the input shaft 40 or to the output shaft 50 or simultaneously with both the input shaft 40 and the Output shaft 50 to connect rotationally fixed, as will be discussed in more detail below with reference to FIGS. 2 and 3.
  • two adjacent switching devices 31, 32 and 33, 35 and 34, 36 are connected in pairs, as is also indicated in the first two lines of the switching table of FIGS. 2 and 3.
  • Another advantage of the change gear 1 10 according to the invention is that only with one of (N-1) gear changes a double circuit must be performed.
  • the second and the third shift sleeve S2, S3 are engaged to shift the first gear.
  • the second shift sleeve S2 is displaced to the right, so that the switching device 33 of the shift sleeve S2 engages with the third idler gear 13, whereby it is rotatably connected to the input shaft 40.
  • the third shift sleeve S3 is displaced to the left, whereby the fourth switching device 34 engages with the fourth idler gear 14 so that it is non-rotatably connected to the output shaft 50.
  • a torque applied to the transmission input shaft 40 is thus transmitted from the input shaft 40 to the idler gear 13 rotationally fixed to the input shaft 40, from where it is transmitted to the countershaft 60 due to the meshing engagement with the fixed gear 23 , Since in the first gear, the fourth idler gear 14 is rotatably connected to the output shaft 50, the torque from the countershaft 60 finally due to the meshing engagement between the fourth fixed gear 24 and the fourth idler gear 14 to the same and from there to the output shaft 50 transmitted.
  • the second, third and fourth gear are switched in a corresponding manner, in which case, however, the fourth switching device 34 always remains engaged in order to non-rotatably connect the fourth idler gear 14 to the output shaft 50.
  • the third gear in which the fifth idler gear 15 is rotatably connected to the input shaft 40 due to a left shift of the second shift sleeve S2.
  • the fifth idler gear 15 thus serves as a gear for the third gear, in which the torque is transmitted from the input shaft 40 via the fifth idler gear 15 to the countershaft 60.
  • the torque is transmitted from the countershaft 60 via the fourth idler gear 14 back to the output shaft 50, for which reason the fourth idler gear 14 or the corresponding track is marked "Lo", thus is to be expressed that on the idler gear 14, the lower transmission ratio range is switched.
  • the idler gear 15 and the corresponding track are also designated "Hi" for the upper gear ratio range.
  • the fifth idler gear 15 is rotatably connected by a right shift of the third shift sleeve S3 with the output shaft 50, whereby the sixth switching device 36 of the shift sleeve S3 is brought into engagement with the fifth idler gear 15.
  • the fifth gear is now engaged, for example, by the shift sleeve S2 is displaced to the right to make a rotational connection between the third idler gear 13 and the transmission input shaft 40 can.
  • a voltage applied to the transmission shaft 40 torque is thus on the third idler gear 13 due to the meshing engagement with the third fixed gear 23 on the countershaft 60 and from there via the fifth fixed gear 25 and the fifth idler gear 15, which is now rotatably connected to the transmission output shaft 50, transmitted to the transmission output shaft 50.
  • the torque is transmitted back to the output shaft 50 exclusively via the fifth idler gear 15.
  • the first and the fifth and the second switching means 31, 35, 32 is engaged to the torque from the input shaft 40 via the first and fifth and second idler gear 1 first , 15, 12 from the input shaft 40 on.
  • a torque direct transmission (DD) between input shaft 40 and output shaft 50 is made possible.
  • trucks trucks
  • it may be useful, contrary to the illustrated embodiment, to assign the highest transmission ratio (i ges 1, 00) by appropriate dimensioning of the individual gear pairs to the highest efficiency of a torque direct transmission for the highest gear achieve.
  • the fifth idler gear 15 is in the "Lo" translation area of the first four gears functional part of the main transmission 1 12, since the same in the "Lo” translation area is not required for the downstream auxiliary gear 1 14, which in This case is formed only by the two meshing wheels 14, 24.
  • the fifth idler gear 15 is a functional component of the downstream additional gear 1 14, wherein in the "Hi" transmission range of the upper four gears, the torque is transmitted to the output shaft 50 via the fifth idler gear 15.
  • the fifth idler gear 15 thus has a double function, which is made possible by the fact that the fifth idler gear 15 in the "Lo" transmission range is not required for torque transmission to the output shaft 50.
  • the first four idler gears 1 1, 12, 13, 14 on the first and the second shaft 40, 50 are.
  • the first four idler gears 1 1, 12, 13, 14 may in principle also be arranged on the countershaft 60, or it may be arranged on the countershaft one or more of the idler gears on the first and second shaft and the other idler gears.
  • the fourth and sixth switching means 34 and 36 may be formed by a common switching means such as a two-way shift sleeve, when the fourth gear 14 is rotatably mounted on the second shaft 50 idler gear, as in this case, the fourth switching device 34 for rotationally fixed connection of the fourth gear 14 with the second shaft 50 adjacent to the sixth switching device 36 is located.
  • a common switching means such as a two-way shift sleeve
  • the transmission of the illustrated embodiment can be switched in the manner explained eight forward gears. However, if, for example, the torque transmission between the first idler gear 13 and the associated fixed wheel 23 takes place indirectly via an intermediate gear, six forward and two reverse gears can be switched with the transmission.
  • the transmission can be combined with another gear stage (such as a switchable planetary gear reducer) to provide 12, 16 or even 20 gears, for example for truck applications.
  • another gear stage such as a switchable planetary gear reducer

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

Abstract

L'invention concerne une boîte de vitesses (100) à au moins huit vitesses, comprenant au moins : - un premier arbre (40) muni d'au moins une première, une deuxième et une troisième roues dentées (11, 12, 13) ; - un second arbre (50) qui est orienté axialement au premier arbre (40) et qui comporte une quatrième roue dentée (14) ; - une cinquième roue dentée (15) qui est orientée coaxialement aux première à quatrième roues dentées (11, 12, 13, 14) et qui est disposée entre les premier et second arbres (40, 50) ; - un arbre intermédiaire (60) muni d'au moins cinq roues dentées antagonistes (21, 22, 23, 24, 25) qui sont chacune en prise au moins indirectement avec l'une des première à cinquième roues dentées (11, 12, 13, 14, 15) afin de former des première, deuxième, troisième, quatrième et cinquième paires de roues dentées ; - des premier, deuxième, troisième et quatrième moyens de changement de vitesse (31, 32, 33, 34), chacune des roues dentées des première à quatrième paires de roues dentées étant une roue fixe, et l'autre roue dentée de chaque paire de roues dentées étant une roue folle qui peut être reliée solidairement en rotation à l'arbre (40, 50), sur lequel elle est disposée, à l'aide du moyen de changement de vitesse (31, 32, 33, 34) respectif ; et - des cinquième et sixième moyens de changement de vitesse (35, 36) qui permettent de relier solidairement en rotation la cinquième roue dentée (15), conçue en roue folle, au choix au premier arbre (40) ou au second arbre (50) ou à la fois au premier et au second arbre (40, 50).
PCT/EP2014/073819 2014-01-29 2014-11-05 Boîte de vitesses à au moins huit vitesses avant WO2015113660A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112014006297.9T DE112014006297A5 (de) 2014-01-29 2014-11-05 Wechselgetriebe zur Realisierung von zumindest acht Vorwärtsgängen

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014201552 2014-01-29
DE102014201552.9 2014-01-29

Publications (1)

Publication Number Publication Date
WO2015113660A1 true WO2015113660A1 (fr) 2015-08-06

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PCT/EP2014/073819 WO2015113660A1 (fr) 2014-01-29 2014-11-05 Boîte de vitesses à au moins huit vitesses avant

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WO (1) WO2015113660A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110249160A (zh) * 2017-02-08 2019-09-17 斯堪尼亚商用车有限公司 用于车辆的变速箱
CN111322361A (zh) * 2019-11-29 2020-06-23 福建中维动力科技股份有限公司 一种八挡变速器变速控制系统

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2822617A1 (de) * 1978-05-24 1979-11-29 Daimler Benz Ag Schaltgetriebe in vorgelegebauart
WO2000004302A2 (fr) * 1998-07-13 2000-01-27 Zf Friedrichshafen Ag Systeme de boite de vitesses

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2822617A1 (de) * 1978-05-24 1979-11-29 Daimler Benz Ag Schaltgetriebe in vorgelegebauart
WO2000004302A2 (fr) * 1998-07-13 2000-01-27 Zf Friedrichshafen Ag Systeme de boite de vitesses

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110249160A (zh) * 2017-02-08 2019-09-17 斯堪尼亚商用车有限公司 用于车辆的变速箱
US11193568B2 (en) * 2017-02-08 2021-12-07 Scania Cv Ab Gearbox for vehicles
CN111322361A (zh) * 2019-11-29 2020-06-23 福建中维动力科技股份有限公司 一种八挡变速器变速控制系统

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Publication number Publication date
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