WO2015197590A1 - Boîte de vitesses à convertisseur différentiel - Google Patents

Boîte de vitesses à convertisseur différentiel Download PDF

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Publication number
WO2015197590A1
WO2015197590A1 PCT/EP2015/064059 EP2015064059W WO2015197590A1 WO 2015197590 A1 WO2015197590 A1 WO 2015197590A1 EP 2015064059 W EP2015064059 W EP 2015064059W WO 2015197590 A1 WO2015197590 A1 WO 2015197590A1
Authority
WO
WIPO (PCT)
Prior art keywords
transmission
power branch
gear
output
mechanical power
Prior art date
Application number
PCT/EP2015/064059
Other languages
German (de)
English (en)
Inventor
Gerhard Meier-Burkamp
Original Assignee
Voith Patent Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Voith Patent Gmbh filed Critical Voith Patent Gmbh
Publication of WO2015197590A1 publication Critical patent/WO2015197590A1/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
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion

Definitions

  • the present invention relates to a differential converter transmission for a motor vehicle, in particular passenger car, bus or truck, but is also applicable to other vehicles, such as rail vehicles.
  • Differential converter transmissions of the generic type are characterized in that drive power from a transmission input via a first hydrodynamic power branch with a hydrodynamic converter and a second mechanical power branch, which is provided in terms of the drive power flow parallel to the first hydrodynamic power branch, can be transmitted to a transmission output, advantageously with a simultaneous power transmission in certain operating states both on the first hydrodynamic power branch and the second mechanical power branch.
  • the present invention is therefore based on the object to further develop the above-mentioned differential converter transmissions for a motor vehicle so that they can be driven in a significantly larger usable driving range with purely mechanical power transmission, the gradation between the individual mechanical gears are smaller than previously executed can be to adjust the lossy transient less frequently and on the other to reduce fuel consumption and noise.
  • An inventive differential converter transmission has a transmission input and a transmission output in order to transmit from the transmission input drive power in different gear ratios to the transmission output, which differ in the rule from each other by their torque-speed ratio.
  • a purely hydrodynamic and / or combined hydrodynamic-mechanical power transmission takes place in some gear stages, and in other gear stages a purely mechanical power transmission takes place from the transmission input to the transmission output.
  • a first hydrodynamic power branch is provided, in which a hydrodynamic converter with at least one impeller, at least one turbine wheel and at least one impeller is arranged, the impeller is connected to the transmission input or connectable and the turbine wheel is connected to the transmission output or connectable to drive power hydrodynamically transmitted via the first hydrodynamic power branch from the transmission input to the transmission output.
  • a second mechanical, in particular purely mechanical power branch is provided, which is connected to the transmission input and the transmission output in the drive power flow parallel to the first hydrodynamic power branch or connectable to transfer drive power mechanically, in particular purely mechanically from the transmission input to the transmission output.
  • a third mechanical power branch is provided, which is connected or connectable to the transmission input and the transmission output to transmit drive power mechanically, in particular purely mechanically from the transmission input to the transmission output at least partially parallel to the first hydrodynamic power branch and the second mechanical power branch.
  • the third mechanical power branch is non-rotatably connected to a transmission input shaft forming the transmission input.
  • the second mechanical power branch has an output shaft connected at least indirectly to the gear output, which is positioned in particular coaxially to a through shaft forming the third mechanical power branch, the output shaft of the second mechanical power branch and the third mechanical power branch are connected together via a coupling gear on the transmission output.
  • the coupling gear not only the drive power from the second and third mechanical power branch can be advantageously combined or added to each other, but advantageously in the coupling gear different translations between the coupling transmission inputs to which the mechanical power branches are connected, and the coupling gear output to which the transmission output is connected, optionally set or switched.
  • the turbine wheel of the hydrodynamic converter via a planetary gear, in particular with a following freewheel, connected to the output shaft of the second mechanical power branch.
  • An alternative embodiment provides that the turbine wheel is connected directly via a freewheel on the output shaft of the second mechanical power branch. Other embodiments are possible, with or without freewheel.
  • the aforementioned planetary gear can also be referred to as a turbine gear, wherein the impeller is connected for example to the sun gear of the planetary gear and the output shaft of the second mechanical power branch, in particular via the freewheel, is connected to the planet carrier or the ring gear.
  • the impeller is connected for example to the sun gear of the planetary gear and the output shaft of the second mechanical power branch, in particular via the freewheel, is connected to the planet carrier or the ring gear.
  • the coupling mechanism can advantageously be designed as a planetary gear, that is, one or more not only on their longitudinal axis but also on a common axis of rotation rotating waves that carry, for example, one or more planetary gears, sun gears and / or ring gears.
  • the output shaft of the second mechanical power branch and the third mechanical power branch via detachable couplings are connected in particular via at least three releasable couplings on the coupling gear.
  • the output shaft of the second mechanical power branch can be coupled via a first releasable coupling and a second releasable coupling to the coupling gear
  • the third mechanical power branch can be coupled via a third releasable coupling to the coupling gear.
  • the coupling gear can be designed, for example, as a multi-shaft planetary gear, in particular four-shaft gear, wherein particularly advantageously at least one or more shafts by means of an associated brake or by means of jointly associated brakes is stopped / is.
  • the impeller of the hydrodynamic converter via a planetary gear is connected to the transmission input, comprising a with the transmission input, in particular purely mechanically, connected ring gear, connected to the impeller, in particular purely mechanically connected sun gear and a planet carrier, wherein the planet carrier, in particular purely mechanically, is connected to the output shaft of the second mechanical power branch.
  • the planetary gear may have the function of an input differential gear, wherein the third mechanical power branch may be connected to the drive side of such an input differential gear.
  • an input differential gear can be provided in a different form than a planetary gear to divide the drive power of the gear on the first hydrodynamic power branch and the second mechanical power branch and in particular the third mechanical power branch.
  • the third mechanical power branch in particular the drive shaft is connected to the ring gear of the aforementioned planetary gear, in particular purely mechanically.
  • the aforementioned ring gear can be selectively stopped by means of a sun gear brake associated with it.
  • the coupling mechanism can have at least one planetary gear, in turn comprising at least one sun gear, at least one planet carrier and at least one ring gear.
  • a plurality of planetary gear for the formation of the linkage are connected in series.
  • the coupling mechanism has according to one embodiment, a web output.
  • the coupling gear on a Hohlradabtrieb The respective output is connected to the transmission output, in particular formed by a transmission output shaft, for example purely mechanically.
  • a hydrodynamic retarder is provided on or within the transmission. Within the transmission may mean that the hydrodynamic retarder is enclosed by the transmission housing, that is positioned within the transmission housing. On the gear can mean that the hydrodynamic retarder is at least partially supported by the gear housing within this or outside of this.
  • the hydrodynamic retarder which has a rotor and a stator or a rotor or a counter-rotating rotor for the formation of a working space which can be filled with a working medium or from this is formed, driven by the transmission output, in particular the transmission output shaft to hydrodynamically decelerate the transmission output and the transmission output shaft.
  • the ratios formed by the differential converter transmission between the transmission input and the transmission output ratios of 0.5, in particular 0.7 to a maximum of 5.0, in particular 4.0.
  • Figure 1 shows a first embodiment of an inventive
  • Figure 2 shows a second embodiment without such a turbine transmission
  • Figure 3 shows a third embodiment of an inventive
  • FIG. 1 shows a coupling structure of an exemplary embodiment of a differential converter transmission according to the invention, which has a hydrodynamic converter 1 with a pump wheel 2, a turbine wheel 3 and a stator 4 for forming the first hydrodynamic power branch 5.
  • the hydrodynamic converter can be designed, for example, as a counter-rotating converter, that is to say that the impeller 2 rotates in operation in the opposite direction to the turbine wheel 3.
  • an embodiment with the same direction rotating paddle wheels is possible, that is, the Impeller 2 and the turbine wheel 3 rotate in the same direction.
  • the stator 4 is held stationary.
  • the first hydrodynamic power branch 5 has a second mechanical power branch 6 and a third mechanical power branch 7 connected in parallel.
  • Drive power can be transmitted from a transmission input 8 to a transmission output 9 via all three power branches 5, 6, 7.
  • the transmission input 8 is formed by a transmission input shaft 10
  • the transmission output 9 is formed by a transmission output shaft 1 1.
  • Transmission input shaft 10 and transmission output shaft 1 1, for example, positioned coaxially to each other, but not mandatory.
  • the transmission input shaft 10 is connected via a planetary gear 12 to the first hydrodynamic power branch 5 and to the second mechanical power branch 6.
  • the transmission input shaft 10 is connected directly to the ring gear 13, which thus forms the input of the planetary gear 12
  • the first hydrodynamic power branch 5 is connected to the sun gear 14 of the planetary gear 12, which thus forms a first planetary gear output
  • the second mechanical power branch 6 is on the planet carrier 15 connected, which thus forms a second planetary gear output of the planetary gear 12.
  • the planetary gear 12, also referred to as the first planetary gear thus operates as a differential gear, which divides the drive power of the transmission input 8 to the first hydrodynamic power branch 5 and the second mechanical power branch 6.
  • the planet carrier 15 carries at least one planet gear 16 which meshes with the sun gear 14 and the ring gear 13. Inn shown embodiment, the sun gear 14 and thus simultaneously the impeller 2 of the hydrodynamic converter 1 by means of a first brake 17 can be stopped to turn off the hydrodynamic power transmission.
  • the turbine wheel 3 of the hydrodynamic converter 1 is connected via a second planetary gear, in the present case referred to as turbine transmission 18, via a freewheel 19 to an output shaft 20 of the second mechanical power branch 6.
  • the turbine transmission 18 has a sun gear 21, a ring gear 22, a planet carrier 23 and at least one planet gear 24.
  • the sun gear 21 is connected to and driven by the turbine wheel 3.
  • the planet carrier 23 is connected via the freewheel 19 with the output shaft 20 of the second mechanical power branch 6.
  • the output shaft 20 of the second mechanical power branch 6 can be connected via a first clutch 25 and / or a second clutch 26 to a coupling gear 27.
  • the third mechanical power branch 7, which comprises, for example, a drive shaft 28 or consists of this, can be connected via a third clutch 29 to the coupling gear 27.
  • the coupling mechanism 27 has in the illustrated embodiment, a third planetary gear 30 and a fourth planetary gear 31.
  • the third planetary gear 30 has a sun gear 32 which is connected to the secondary side of the second clutch 26, also a planet carrier 33, which carries at least one planet gear 34, and a ring gear 35, which rotatably or mechanically with the planet carrier 36 of the fourth planetary gear 31 connected is.
  • the fourth planetary gear 31 has a sun gear 38 which is non-rotatably connected to the secondary side of the third clutch 29.
  • the planet carrier 36 carries on the one hand at least one planetary gear 39 of the fourth planetary gear 31 and on the other hand at least one planetary gear 40, which meshes with a sun gear 41 which is non-rotatably connected to the planet carrier 33 of the third planetary gear 30.
  • the planetary gear 39 and the planetary gear 40 are designed as a component or a common planetary gear.
  • the sun gears 38 and 41 have the same number of teeth.
  • the planet carrier 36 of the fourth planetary gear 31 is further rotatably connected to a planet carrier 42 which carries at least one planet gear 43 which meshes with a sun gear 44, which in turn is rotatably connected to the secondary side of the first clutch 25.
  • the planetary gear 43 advantageously meshes with the planetary gear 39, 40th
  • the planet carrier 36 of the fourth planetary gear 31 is also rotatably connected to the transmission output 9, formed here by the transmission output shaft 1 1, which drives the rotor 45 of a hydrodynamic retarder 46 in the illustrated embodiment and / or carries, which forms a common working space with the stator 47.
  • the second clutch 26 and the third clutch 29 can be selectively coupled to the linkage 27, wherein the sun gear 32 of the third planetary gear 30 can be stopped by a second brake 48 and the planet carrier 33 of the third planetary gear 30 can be stopped by a third brake 49, six mechanical forward gears and a mechanical reverse gear can be realized with the coupling structure shown.
  • the reverse gear and the first three or in particular four mechanical gears allow use of the hydrodynamic converter 1 as a wear-free starting element.
  • this area of the coupling structure is also referred to as a bar output, with the word "bar" as an alternative name for planet carrier.
  • corresponding elements are designated by corresponding reference numerals.
  • the difference to the embodiment according to FIG. 1 lies solely in the fact that the turbine transmission 18 has been dispensed with as the second planetary gear and the turbine wheel 3 is connected via the freewheel 19 directly to the output shaft 20 of the second mechanical power branch 6, which due to their connection to the planet carrier 15 of the first planetary gear 12, also referred to as input differential, can also be referred to as a ridge wave of the input differential.
  • the exemplary embodiment according to FIG. 3 differs solely from the exemplary embodiment of FIG. 1 in that the coupling mechanism 27 is connected via a ring gear output to the transmission output 9 or the transmission output shaft 1 1. For this purpose, a transformation of the linkage 27 is necessary.
  • the sun gear 32 of the third planetary gear 30 can be stopped.
  • the ring gear 35 of the third planetary gear 30 is rotatably connected to the transmission output 9 and the transmission output shaft 1 1 connected.
  • the planet carrier 33 with the at least one planetary gear 34 of the third planetary gear 30 rotates together with the planet carrier 36 of the fourth planetary gear 31 and is therefore connected to this accordingly.
  • the planet carrier 36 carries the at least one planetary gear 39, which meshes with the sun gear 38.
  • the sun gear 38 can be coupled via the first clutch 25 to the output shaft 20 of the second mechanical power branch 6.
  • the sun gear 32 of the third planetary gear 30 can be coupled via the second clutch 26 to the output shaft 20.
  • the planet carrier 36 of the fourth planetary gear 31 can be coupled via the third clutch 29 to the drive shaft 28 of the third mechanical power branch 7.
  • the other planetary gear 37 on the planet carrier 36 but in particular, however, the planetary gears 39 and 37 are designed as a component or a common planetary gear, combs advantageous also with the planet gear 34th
  • the first brake 17 can be closed to form a purely mechanical gear, or be opened to use the hydrodynamic power transmission.
  • the hydrodynamic converter 1 can be used as a starting element for accelerating the motor vehicle or the transmission output 9.
  • the first clutch 25 is closed, the second clutch 26 is opened, the third clutch 29 is opened, the second brake 48 is opened and the third brake 49 is closed.
  • the second brake 48 may be closed in the second forward gear and the third brake 49 may be open.
  • the first clutch 25 and the second clutch 26 may be closed, the second brake 48, the third brake 49 and the third clutch 29 may be open.
  • the first clutch 25 and the third clutch 29 may be closed, the second clutch 26 and the second brake 48 and the third brake 49 may be open.
  • the first brake 17 is usually closed.
  • the first clutch 25 is further opened, the second clutch 26 is closed, the second brake 48 and the third brake 49 are open and the third clutch 29 is closed.
  • the first clutch 25 and the second clutch 26 are in particular open, and the second brake 48 is closed, the third brake 49 is opened and the third clutch 29 is closed.
  • reverse gear are advantageously the first clutch 25 and the first brake 48 and the third clutch 29 is opened, whereas the second clutch 26 and the third brake 49 are closed.
  • the first brake 17 is open during the power transmission via the first hydrodynamic power branch 5 for starting, but can also be closed to transmit only drive power via the second mechanical power branch 6 and the second mechanical power branch 6 and the third mechanical power branch 7.

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

Abstract

L'invention concerne une boîte de vitesses à convertisseur différentiel, destinée à un véhicule automobile, en particulier une voiture de tourisme, un bus ou un camion, qui comprend une entrée de transmission (8) et une sortie de transmission (9). La boîte de vitesses comprend également une première branche de puissance hydrodynamique (5) dans laquelle est disposé un convertisseur hydrodynamique pourvu d'une roue de pompe (2), d'une roue de turbine (3) et d'un stator (4), dont la roue de pompe est ou peut être reliée à l'entrée de transmission, et dont la roue de turbine est ou peut être reliée à la sortie de transmission afin de transmettre la puissance d'entraînement de l'entrée de transmission à la sortie de transmission de manière hydrodynamique par le biais de la première branche de puissance hydrodynamique. La boîte de vitesses comporte en outre une deuxième branche de puissance mécanique (6) qui est ou peut être reliée à l'entrée de transmission et à la sortie de transmission parallèlement à la première branche de puissance hydrodynamique par référence au flux de puissance d'entraînement afin de transmettre mécaniquement de la puissance d'entraînement de l'entrée de transmission à la sortie de transmission. La boîte de vitesses à convertisseur différentiel de l'invention est caractérisée par une troisième branche de puissance mécanique (7) qui est ou peut être reliée à l'entrée de transmission et à la sortie de transmission afin de transmettre mécaniquement de la puissance d'entraînement de l'entrée de transmission à la sortie de transmission au moins partiellement parallèlement à la première branche de puissance hydrodynamique et à la deuxième branche de puissance mécanique.
PCT/EP2015/064059 2014-06-24 2015-06-23 Boîte de vitesses à convertisseur différentiel WO2015197590A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014212052.7 2014-06-24
DE102014212052.7A DE102014212052A1 (de) 2014-06-24 2014-06-24 Differentialwandlergetriebe

Publications (1)

Publication Number Publication Date
WO2015197590A1 true WO2015197590A1 (fr) 2015-12-30

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ID=53476894

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/064059 WO2015197590A1 (fr) 2014-06-24 2015-06-23 Boîte de vitesses à convertisseur différentiel

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DE (1) DE102014212052A1 (fr)
WO (1) WO2015197590A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107504151B (zh) * 2017-10-12 2024-04-26 中国船舶重工集团公司第七0三研究所 一种功率多分支液力行星调速装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2919604A (en) * 1957-07-26 1960-01-05 Gen Motors Corp Transmission
US3605522A (en) * 1967-11-22 1971-09-20 Citroen Sa Drive units
EP0014139A2 (fr) * 1979-01-23 1980-08-06 Gérard Plas Transmission à variation continue du rapport de transmission

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2214648C2 (de) 1970-05-02 1984-09-06 J.M. Voith Gmbh, 7920 Heidenheim Leistungsverzweigendes, mit einer Bremsschaltung versehenes hydrodynamisch-mechanisches Getriebe
US20110179891A1 (en) * 2007-09-20 2011-07-28 Busch Jorg Automatic transmission having hydrodynamic converter
DE102008010064B4 (de) 2008-02-20 2016-04-07 Voith Patent Gmbh Automatgetriebe mit wenigstens einem Planetensatz
DE102008027946A1 (de) 2008-06-12 2009-12-24 Voith Patent Gmbh Automatgetriebe mit einem Antriebsbereich, einem hydrodynamischen Wandler, und einem Abtriebsbereich sowie Verfahren zum Bremsen bei hohen Drehzahlen

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2919604A (en) * 1957-07-26 1960-01-05 Gen Motors Corp Transmission
US3605522A (en) * 1967-11-22 1971-09-20 Citroen Sa Drive units
EP0014139A2 (fr) * 1979-01-23 1980-08-06 Gérard Plas Transmission à variation continue du rapport de transmission

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Publication number Publication date
DE102014212052A1 (de) 2015-12-24

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