EP1664592A1 - Module de boite de vitesses - Google Patents

Module de boite de vitesses

Info

Publication number
EP1664592A1
EP1664592A1 EP04764724A EP04764724A EP1664592A1 EP 1664592 A1 EP1664592 A1 EP 1664592A1 EP 04764724 A EP04764724 A EP 04764724A EP 04764724 A EP04764724 A EP 04764724A EP 1664592 A1 EP1664592 A1 EP 1664592A1
Authority
EP
European Patent Office
Prior art keywords
gear
output
countershaft
transmission
power
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.)
Withdrawn
Application number
EP04764724A
Other languages
German (de)
English (en)
Inventor
Werner Klement
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.)
Voith Turbo GmbH and Co KG
Original Assignee
Voith Turbo GmbH and 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 Voith Turbo GmbH and Co KG filed Critical Voith Turbo GmbH and Co KG
Publication of EP1664592A1 publication Critical patent/EP1664592A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F16H3/097—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 the input and output shafts being aligned on the same axis
    • 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
    • F16H3/12—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 with means for synchronisation not incorporated in the clutches
    • 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
    • F16H3/12—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 with means for synchronisation not incorporated in the clutches
    • F16H3/126—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 with means for synchronisation not incorporated in the clutches using an electric drive
    • 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
    • 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
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by parallel flow paths, e.g. dual clutch transmissions
    • F16H2003/007—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by parallel flow paths, e.g. dual clutch transmissions with two flow paths, one being directly connected to the input, the other being connected to the input through a clutch
    • 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
    • F16H2003/0933—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 coaxial countershafts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19149—Gearing with fluid drive
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19223—Disconnectable counter shaft
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19233—Plurality of counter shafts

Definitions

  • the invention relates to a transmission assembly, in particular an automatic transmission in detail with the features from the preamble of claim 1.
  • Gear units in particular automatic gearboxes, are known from the prior art in a large number of very different designs.
  • these include a starting element, a lock-up clutch assigned to this, and a speed / torque conversion unit arranged after the start-up element and the lock-up clutch, which is characterized by at least one gear stage.
  • All transmission modules have in common that during the switching process, ie. H. in particular a gear change no pull power interruption is present. This means that the shifting element to be released of the outgoing gear stage and the gear element to be closed of the upcoming, i.e. H. at least one part of the power provided by the drive machine is transmitted overlapping one another.
  • the shifting elements are operated with slip, which is why only non-positive shifting elements, in particular those that are transmitted via frictional engagement, are generally used here.
  • this has the disadvantage that, on the one hand, due to the slippery mode of operation of the individual switching elements during power transmission between the transmission input and the transmission output, power losses are recorded, which is why the efficiency of the overall unit is low, and furthermore the individual switching elements are subject to wear and thus short maintenance intervals for the entire unit require. If synchronously switchable clutches are used, the shifting always takes place with traction interruption.
  • the invention has for its object to further develop a transmission assembly of the type mentioned in such a way that the disadvantages mentioned are avoided. In particular, there is no need for wear-prone transmission elements in the power flow.
  • the solution according to the invention is characterized by the features of claim 1. Advantageous refinements are given in the subclaims.
  • the gear unit includes at least one gear input and one gear output.
  • a starting element is provided between these and a device for changing gear associated with the starting element is provided. In addition to the bridging function for the starting element, this also maintains the tractive force during the gear change.
  • Speed is also provided
  • the starting element itself has at least one input that is non-rotatably connected to the transmission input and one output that is at least indirectly non-rotatably connectable to the transmission output, this connection being realized in part only via the gear change device.
  • the device for changing gear comprises at least two inputs, a first input which is connected in a rotationally fixed manner to the output of the starting element and a second input which is connected in a rotationally fixed manner to the input of the starting element, this connection being free of a rotationally fixed coupling to the output of the Starting element is. So that at least one output is provided, which is connected to the transmission output.
  • Each input of the gear change device can optionally be connected via a synchronously switchable clutch to the output of the gear change device to form two power branches, a first power branch and a second power branch.
  • the synchronously switchable clutches can either be used together in the sense of Realization of a rotationally fixed connection between the respective input and the output to be operated or individually. This makes it possible, on the one hand, to carry out the power transmission in two power branches, the power transmission taking place via the starting element in the first power branch, while a purely mechanical one is carried out in the second power branch
  • Power transmission is carried out by the transmission input is rotatably connected to the output of the gear change device bypassing the starting element.
  • the power can be transmitted in parallel via both branches, the gear change device in this case functioning as a summing gear and both power branches being brought together again at the output of the gear change device.
  • the required installation space can be kept to a minimum or the installation space freed up compared to the solution proposed according to a) can be used for the arrangement of other functional elements.
  • the basic configuration according to the invention of the starting element, device for changing gear and speed / torque conversion device also enables the operation as a gear unit in the form of an automatic transmission also the operation as an automated manual transmission, whereby no changes and modifications are necessary, but only a change in the control must be made, since in this case there is always a separation between the engine and the transmission during the switching process he follows.
  • This change in the control includes the exclusion of the power transmission via the first power branch during the switching process, ie there is no power transmission via the starting element.
  • the structural design takes the form of a countershaft construction.
  • Each power branch has at least one first countershaft, which is connected to the output of the starting element or the input of the starting element in a rotationally fixed manner, and again via a further countershaft which can be coupled to a countershaft arranged parallel to the starting element, in particular to the axis of rotation of the starting element, with the output of the device is connected to change gear.
  • the synchronously switchable clutch is arranged between the countershaft, which is connected to the output of the device for changing gear, and the countershaft.
  • the individual countershafts are arranged in the axial direction parallel to one another and coaxially with one another, one of the two countershafts being designed as a hollow shaft through which the other
  • the device for changing gear itself can already characterize a gear stage and thus forms part of the speed / torque conversion device or parts of the speed
  • the speed / torque conversion device arranged downstream of the device for changing gear is also designed in countershaft construction, so that the countershaft of the second power branch can also be used here.
  • the space requirement can be kept very low.
  • the bridging function can thereby also directly into the
  • Gears are integrated so that the output of the gear change device is formed at any point in the transmission in this case.
  • the transmission designed according to the invention is free of frictional power transmission, so that wear-prone ones
  • the synchronously switchable clutches are preferably designed as positive clutches, in particular claw clutches.
  • Hydrodynamic components are conceivable, for example hydrodynamic clutches or converters, energy source-generator units as well as hydrostatic but also mechanical (wet or dry multi-plate clutches) solutions.
  • hydrodynamic clutches or converters for example hydrodynamic clutches or converters, energy source-generator units as well as hydrostatic but also mechanical (wet or dry multi-plate clutches) solutions.
  • the transmission assembly according to the invention thus comprises only one transmission element with slip in the form of the starting element. In all other gear stages, the power transmission is purely mechanically free of slip. To implement the bridging of the hydrodynamic element and a gear stage, only a single clutch is required and not several that have to be engaged at the same time.
  • FIG. 1 illustrates in a schematically simplified representation the basic structure of a transmission module designed according to the invention, which can also be used as an automated manual transmission by changing the control;
  • FIGS. 2a-2f illustrate in a schematically simplified representation using a particularly advantageous embodiment according to FIG. 1 the functioning of the gear unit designed according to the invention in the individual operating states
  • Figure 3 illustrates an embodiment with coaxially arranged present.
  • FIG. 1 illustrates the basic structure and the basic principle of a design according to the invention in a schematically simplified representation
  • Gear unit in particular an automatic transmission.
  • This comprises at least one transmission input E and one transmission output A.
  • a starting element 2 and a device assigned to this for changing gear, in particular bridging the starting element and maintaining the tractive force during the gear stage change.
  • a transmission assembly 1 comprises at least one speed / torque conversion device 4, preferably in the form of so-called shift stages.
  • the starting element 2 and the bridging coupling for bypassing the power flow at the starting element 2 are each connected to the transmission input E and also at least indirectly to the transmission output A.
  • the starting element 2 has an input 5 which is connected to the transmission input E or forms it ,
  • the starting element 2 also has an output 6 which is at least indirectly connected to the transmission output A. At least indirectly means that usually further speed
  • the device for changing gear 3 comprises at least one output 9, which is at least indirectly non-rotatably connected to transmission output A.
  • the coupling to the transmission output A takes place via at least one speed / torque conversion device 4.
  • the starting element 2 is also via the
  • Start-up element 2 and device for changing gear 3 can be designed as separate structural units that are coupled to one another or can be combined to form a structural unit.
  • Gear changes 3 have already been combined with the downstream speed / torque conversion devices 4 and only combined with the starting element 2 to form the overall structural unit transmission unit 1.
  • the device for changing gear 3 Due to the connection of the device for changing gear 3 in the version with two inputs 7 and 8, it is possible to implement two power branches in the interaction of starting element 2 and device for changing gear 3.
  • the first power branch which is referred to here as 10
  • the power is carried from the transmission input E to the transmission output A via the starting element 2 and the device for gear change 3 arranged downstream thereof.
  • the second power branch which is referred to here as 10
  • the power is carried from the transmission input E to the transmission output A via the starting element 2 and the device for gear change 3 arranged downstream thereof.
  • Power branch 11 leads the power flow bypassing the starting element 2 to the transmission output A via the gear change device 3. Both power branches can be switched separately or in parallel.
  • the first power branch 10 is structurally characterized by the coupling between the transmission input E and the input 7 of the device for changing gear 3 via the starting element 2 and the device for changing gear 3 with the output A.
  • the second power branch 11 is through the coupling characterized between the transmission input E and the device for gear change 3 with the transmission output A.
  • both power branches 10 and 11 can be activated individually or in parallel via a synchronously switchable clutch 16 and 17 which is arranged in each power branch 10 and 11 and can be actuated optionally.
  • the synchronously switchable clutches 16 and 17 serve the at least indirect, ie. H. either or via additional transmission elements that can be produced in a rotationally fixed connection between the individual input 7, 8 of the device for changing gear 3 and the output 9 thereof.
  • the power flow takes place in the individual power branches 10, 11 at least partially parallel to the axis of rotation of the starting element 2.
  • the gear change device 3 has at least two additional gears, a first additional gear 12 and a second additional gear 13, the first additional gear 12 being connected to the output 6 of the starting element 2, while the second additional gear 13 is connected to the transmission input E or the rotationally fixedly connected input 5 of the starting element 2 in the power flow direction before the output 6 of the starting element 2.
  • the countershaft - the first countershaft 12 and the second countershaft 13 - can each be connected at least indirectly to the output 9 of the gear change device 3 and thus to the transmission output A via the synchronously switchable clutch 16 or 17.
  • the coupling is preferably carried out via a further reduction gear 18 or 19 arranged coaxially with the respective reduction gear, in particular the first reduction gear 12 and the second reduction gear 13.
  • each of the outputs 14 or 15 of the reduction gear 12 or 13 is rotatably fixed with a reduction shaft 20 or 21 connected, which in turn can be coupled via the synchronously switchable clutches 16 and 17 to the corresponding additional countershaft 18 and 19, respectively.
  • Gear change 3 thus has two countershafts 20 and 21, which are arranged parallel to the transmission input E or transmission output A and which operate via the Gears 18 and 19 can be connected to the transmission output A.
  • the transmission input E and the transmission output A are preferably arranged coaxially with one another. However, this is not absolutely necessary.
  • the device for changing gear 3 is realized by means of the two synchronously switchable clutches 16 and 17, the first synchronously switchable
  • Coupling 16 is used to couple the output 6 of the starting element 2 to the transmission output A, while the second switchable coupling 17 is used to couple the transmission input E or the input 5 of the starting element 2, which is non-rotatably coupled thereto, to the transmission output A.
  • Both synchronously switchable clutches 16 and 17 are arranged parallel to one another in the embodiment shown in FIG. With regard to their translation, the individual countershafts 12, 13 are preferably designed such that they implement at least one translation 1 as a function of the starting element 2 used.
  • the synchronously switchable clutches 16 and 17 are designed as form-fitting clutches, the form-fitting connection preferably being realized by claws.
  • the starting element can be designed in many forms, preferably hydrodynamic components 22 are used.
  • the flow of force is designed according to the desired power transmission via the first or second power branch 10 or 11 alone or else via both power branches 10 and 11 together.
  • the power is transmitted solely via the first power branch 10, that is to say the starting element 2.
  • the power is considered in traction mode from the transmission input E to the transmission output A from the transmission input E via the starting element 2, the output of the Transfer element 2 to the first countershaft 12 and, when the switchable clutch 16 is actuated, to the further countershaft 8, which is at least indirectly non-rotatably coupled to the transmission output A, that is to say, for example, via further speed / torque conversion devices 4.
  • the second synchronously switchable clutch 17 is in its shift position 11, which describes the opened state.
  • the second power branch is used to bypass 11 activated, in which state the power transmission takes place at least partially via the starting element 2 and thus the first power branch 10.
  • a moment is still passed to the output shaft or the transmission output A during the switching process.
  • This is controlled by the brief activation of the hydrodynamic component.
  • For an upshift this is as follows: When driving in gear x, the power is transmitted purely mechanically via the switchable clutch, in particular the claw, which provides a rigid connection between the engine and the transmission. Before the switching process, the hydrodynamic component is filled and now transmits a torque during a switching process y.
  • the claw that was previously transmitting ie the switching element to be released
  • the claw that was previously transmitting is released and is opened.
  • the engine ie the drive machine
  • the claw of the new gear that is to say the gear that is to be or is to be engaged
  • the gearshift is ended.
  • the second synchronously switchable clutch 17 is switched on, which is then in its switching position 17 and connects the second countershaft 21 to the further fourth countershaft 19 in a rotationally fixed manner.
  • a first power component is transmitted via the first power branch 10 and a second power component via the second power branch 11, in accordance with the design of the individual countershaft, first countershaft 12 of the starting element 2 and third countershaft 18 and the second countershaft 13 and the fourth countershaft 19.
  • the hydrodynamic component 27 must work with slip. It must therefore be ensured that slip is possible with every gear change.
  • FIGS. 2a to 2g illustrate the basic structure and the functioning of a particularly advantageous embodiment of a gear unit assembly 1 designed according to the invention on the basis of a schematically simplified representation.
  • the basic structure corresponds in principle to that described in FIG. 1, which is why the same reference numerals are used for the same elements.
  • a speed / torque conversion device 4 which is characterized by an embodiment with four spur gear stages 23 to 26.
  • This version is exemplary.
  • the design of the spur gear stages 23 to 26 is also of a countershaft design, these being coupled to the second countershaft 13.
  • the individual gear stages are thus assigned to the second power branch 11, in which the power for the device for changing gear 3 is transmitted purely mechanically.
  • Spur gear stages 23 to 26 connected. Furthermore, a further synchronously switchable clutch 27 can be seen, which is arranged between the transmission input E and the transmission output A in a spatial arrangement in the axial direction behind the two gears, first gearing 12 and second gearing 13. This is used for the rigid coupling between gearbox input E and the speed
  • the starting element 2 is designed here as a hydrodynamic component 22, in the illustrated case preferably as a hydrodynamic clutch 28, comprising at least one primary wheel 29 functioning as a pump wheel and acting as a turbine wheel acting as a turbine wheel in traction operation when transmitting power from the transmission input E to the transmission output A.
  • the primary wheel 29 is rotatably connected to the transmission input E or forms it. Furthermore, the primary wheel 29 forms the input of the starting element 2.
  • the secondary wheel 30 forms the output 6 of the starting element 2 and is at least indirectly non-rotatably with the device via the gear change device
  • Gearbox output A can be connected. This means that conditions are conceivable in which the secondary wheel 30 is completely decoupled from the transmission output A.
  • the secondary wheel 30 is connected to the first countershaft 12. This is designed as a simple spur gear set 31, a first spur gear 32 of the spur gear set 31 being connected in a rotationally fixed manner to the secondary gear 30.
  • the coupling with the third countershaft 18 takes place via the synchronously switchable clutch 16, in the case shown in the form of a dog clutch.
  • the first countershaft 12 and the third countershaft 18 are arranged parallel to one another and coaxially to one another.
  • the first countershaft 12 can also be coupled at least indirectly non-rotatably with the fourth countershaft 19, this also takes place via the synchronously switchable clutch 16.
  • this has a further shift position III1 6 , which the countershaft 20 rotatably with the fourth countershaft 19 combines.
  • the procedure also applies in analogy to the second countershaft 13.
  • This is also designed as a spur gear set 34.
  • This comprises a first spur gear 35, which is coupled in a rotationally fixed manner to the transmission input E or the input 5 of the starting element 2 and which meshes with a spur gear 36 which is non-rotatably coupled to the countershaft 21 and forms the output 15 of the countershaft 13.
  • the countershaft 21 is via the synchronously switchable clutch 17 with the fourth countershaft 19 and for realizing a further gear stage alternatively connected to the third countershaft 18.
  • the gear change device 3 is combined directly with the speed / torque conversion device 4, in which case the countershaft 21 is used to implement the gear stages in countershaft construction.
  • the individual meshing gears for implementing the gear stages are designed in the form of spur gear pairs, in which the meshing spur gears can each be connected in a rotationally fixed manner to the transmission output shaft A and the countershaft 21.
  • the specific choice of the connection of the individual spur gears can be made arbitrarily. These can preferably be switched via further
  • Couplings 37 and 38 are either connected in a rotationally fixed manner to the transmission output A or the other spur gear of a spur gear pair on the countershaft 21 via the switchable couplings.
  • the individual additional further gear stages are realized by four countershafts, which are designated 39 to 42 here and by
  • Spur gear sets 23 to 26 are characterized.
  • the spur gears of the individual spur gear sets 23 to 26 are either arranged in a rotationally fixed manner on the countershaft 21 or else a shaft is coupled in a rotationally fixed manner to the transmission output A.
  • the switchable clutch 37 is arranged coaxially with the starting element 2 and thus also coaxially with the transmission input E and the transmission output A and enables the rotationally fixed coupling of the spur gear sets 23 or 24 to the transmission output shaft A via the second power branch 11.
  • the spur gear sets 41 and 42 can be connected to the countershaft 21 via the further switchable clutch 38, with a due to the rotationally fixed connection of the respective spur gears to the transmission output A.
  • This arrangement is characterized by simple construction.
  • the individual spur gear ratios in the individual gears or spur gear stages are designed for the speed
  • the Transmission ratios are set in such a way that a translation of ⁇ 1 is realized here between the input E and the coupling with the speed / torque conversion units.
  • the specific execution is at the discretion of the responsible specialist.
  • a braking device 43 is also provided, which is assigned to the starting element 2, in particular the output 6 of the starting element 2, and thus in the case shown is fixing the secondary wheel 30.
  • the gearbox output A can thus have the appropriate gear ratio, in particular the
  • FIG. 2b illustrates the state of the start-up by way of example using the design of the transmission module 1, in particular the automatic transmission according to FIG.
  • the flow of power is illustrated here by an increased stroke.
  • the device for changing gear 3 is characterized by the shift position III of the synchronously shiftable clutch 16.
  • the first countershaft 12 is connected in a rotationally fixed manner to one of the countershaft, for example the fourth countershaft 19.
  • a connection over 18 would also be conceivable.
  • All other synchronously switchable clutches 37, 38 and 27 and 17 are open in this functional state.
  • the connection of the lockup is shown in the combined starting and switching state in FIG. 2c. It can be seen from this that the power transmission takes place for a short time via two power branches, the power branch 10 and the power branch 11, and no black-and-white
  • the second countershaft 13, in particular the countershaft 21, via any spur gear set, for example here the Transfer spur gear set 25 to gearbox output A.
  • the countershaft 21 is coupled via the switchable clutch 38 to the spur gear set 25 and thus to the countershaft 41. It would also be conceivable, depending on the desired gear stage to be set, to actuate the synchronously shiftable clutch 17, in which case the countershaft 21 is actuated via the fourth
  • Gearbox would be connected to the transmission output A.
  • the power flows of both power branches 10 and 11 are brought together before output A. This is preferably done at the exit of the gear change device 3.
  • FIG. 2d illustrates, by way of example, a purely mechanical power transmission in a specific gear, for example a second gear step, which is characterized by the additional gear 19.
  • the hydrodynamic clutch when the hydrodynamic clutch is emptied, either the synchronously switchable clutch 16 can engage or be coupled to a spur gear set that is not coupled to the countershaft 21, or it can be completely decoupled from the transmission output A in the open state, that is to say in the shift position II.
  • the power is then transmitted from the transmission input E to the transmission output A via the second power branch 11, here, for example, the fourth countershaft 19 by activating the synchronously shiftable clutch 17 and moving it into the shift position 7 , which is characterized by the rotationally fixed connection of the third countershaft 18 to the countershaft 21 ,
  • the power flow for the individual gear stages can be realized by the optional activation of the synchronously switchable clutches 17, 37 and 38, provided that there is no power flow via the first power branch 10.
  • the starting element 2 is coupled to the transmission output A again, for example by switching or actuating the synchronously switchable clutch 16 and connecting the countershaft 20 to the fourth countershaft 18 and thus the transmission output A.
  • Figure 2e shows.
  • the power flow for a short state is again conducted in parallel via the hydrodynamic branch 10 and the purely mechanical branch 11, wherein after the synchronously switchable clutch 16 has been brought into engagement, the shifting element, in the illustrated case the synchronously switchable clutch 17, is opened , In this state, the power flow takes place briefly via the starting element, that is to say the first power branch 10.
  • the corresponding synchronously shiftable clutch for the gear stage to be engaged the coming shifting element, which in the illustrated case is formed by the shiftable clutch 17, is actuated and in their switch position, here the switch position III 17 is spent.
  • the second countershaft 13 is connected to the transmission output A via the third countershaft 18. If the synchronously switchable clutch 17 is in its switching position III 7 , the power flow in the first power branch 10 is interrupted.
  • FIG. 2g illustrates the power transmission in direct gear.
  • the synchronously switchable clutch 27 is actuated. This takes place when the speed of the transmission input E and the transmission output A are the same. All other switchable clutches are open.
  • all clutch devices are designed as synchronously switchable clutches, which preferably operate in a form-fitting manner. Claw clutches are used in a particularly advantageous manner.
  • the gear unit 1 is in terms of the couplings to be implemented in the device for changing gear 3 and in speed
  • FIGS. 1 and 2 Illustrated in FIGS. 1 and 2 are versions with mutually parallel arrangements of the individual switchable clutches 16 and 17 of the device for changing gear 3,
  • FIG. 3 shows a particularly advantageous embodiment with a coaxial arrangement thereof.
  • one of the countershafts 20 or 21 is designed as a hollow shaft. This depends on the arrangement of the reduction gear, first reduction gear 12 and second reduction gear 13 and the spatial arrangement of input 5 and output 6 of the starting element 2. In the case shown is the
  • Countershaft 21 of the second countershaft 13 is designed as a hollow shaft 13 through which the countershaft 20 of the first countershaft 12 is guided. Both gears are arranged coaxially and parallel to each other. The connection of the first countershaft to the transmission output A takes place via the third countershaft 18, which in this case is axially connected to all the counters coupled to the hollow shaft
  • Transmission module starting element device for gear change speed / torque conversion device input of the starting element output of the starting element input of the device for changing gear input of the device for changing gear output of the device for changing gear first power branch second power branch first gear second gear output output output synchronously switchable clutch synchronously switchable clutch further third gear fourth Countershaft countershaft countershaft hydrodynamic component spur gear stage spur gear stage spur gear stage synchronous switchable clutch hydrodynamic clutch primary gear secondary gear 31 spur gear set

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

Abstract

La présente invention concerne un module de boîte de vitesses (1) comprenant une entrée de boîte de vitesses (E), au moins une sortie de boîte de vitesses (A), un élément de démarrage (2) qui est couplé à l'entrée de boîte de vitesses (E) et qui comprend une entrée (5) et une sortie (6) pouvant être couplée au moins indirectement à la sortie de boîte de vitesses (A), ainsi qu'un dispositif de changement de vitesse (3) qui comprend au moins deux entrées (7, 8) et une sortie (9) pouvant être reliée à la sortie de boîte de vitesses (A). Une première entrée (7) du dispositif de changement de vitesse (3) est reliée à la sortie (6) de l'élément de démarrage (2) et une seconde entrée (8) est reliée à l'entrée (5) de l'élément de démarrage (2). Chaque entrée (7, 8) du dispositif de changement de vitesse (3) est respectivement reliée au choix par l'intermédiaire d'un embrayage à commutation synchrone (16), formant une première dérivation de puissance (10) et une seconde dérivation de puissance (11). Les deux embrayages à commutation synchrone (16, 17) permettent respectivement pour eux-mêmes ou conjointement à l'état fermé l'établissement d'un flux de puissance par l'intermédiaire des dérivations de puissance (10, 11).
EP04764724A 2003-09-19 2004-09-02 Module de boite de vitesses Withdrawn EP1664592A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10343972A DE10343972A1 (de) 2003-09-19 2003-09-19 Getriebebaueinheit
PCT/EP2004/009765 WO2005040640A1 (fr) 2003-09-19 2004-09-02 Module de boite de vitesses

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EP1664592A1 true EP1664592A1 (fr) 2006-06-07

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EP04764724A Withdrawn EP1664592A1 (fr) 2003-09-19 2004-09-02 Module de boite de vitesses

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US (1) US7707910B2 (fr)
EP (1) EP1664592A1 (fr)
JP (1) JP2007506047A (fr)
DE (1) DE10343972A1 (fr)
WO (1) WO2005040640A1 (fr)

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EP1664593B1 (fr) * 2003-09-19 2011-08-31 Voith Turbo GmbH & Co. KG Embrayage de pontage pour composants hydrodynamiques
CA2569441C (fr) * 2006-11-30 2011-02-08 Supreme International Limited Systeme de transmission hydrodynamique
DE102007038236A1 (de) 2007-08-13 2009-02-19 Voith Patent Gmbh Kraftfahrzeug-Anfahrelement und Verfahren zum Antreiben eines Kraftfahrzeugs
GB2463911B (en) * 2008-09-30 2012-06-06 Jcb Transmissions Vehicle transmission
DE102010028077A1 (de) * 2010-04-22 2011-10-27 Zf Friedrichshafen Ag Verfahren zur Schaltsteuerung eines automatisierten Schaltgetriebes
KR101293297B1 (ko) * 2011-07-29 2013-08-09 현대 파워텍 주식회사 자동화 수동변속기
DE102012001948A1 (de) * 2012-02-02 2013-08-08 Daimler Ag Doppelkupplungsgetriebe
KR20130116998A (ko) * 2012-04-17 2013-10-25 (주)테너지 자동화 수동 변속기
CN109578530B (zh) * 2017-09-29 2020-11-06 比亚迪股份有限公司 三挡变速器及三挡电动总成
US12228191B2 (en) * 2021-09-03 2025-02-18 Exedy Globalparts Corporation Selectable torque path torque converter architecture
CN118753485A (zh) * 2024-09-06 2024-10-11 杭州萧山江南通用机械有限公司 一种双动力电机外挂式船用齿轮箱

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Also Published As

Publication number Publication date
US20070193382A1 (en) 2007-08-23
DE10343972A1 (de) 2005-04-28
JP2007506047A (ja) 2007-03-15
US7707910B2 (en) 2010-05-04
WO2005040640A1 (fr) 2005-05-06

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