WO1998017926A1 - Transmission a deux contre-arbres - Google Patents

Transmission a deux contre-arbres Download PDF

Info

Publication number
WO1998017926A1
WO1998017926A1 PCT/HU1997/000065 HU9700065W WO9817926A1 WO 1998017926 A1 WO1998017926 A1 WO 1998017926A1 HU 9700065 W HU9700065 W HU 9700065W WO 9817926 A1 WO9817926 A1 WO 9817926A1
Authority
WO
WIPO (PCT)
Prior art keywords
wheels
shaft
odd
torque converter
drive shaft
Prior art date
Application number
PCT/HU1997/000065
Other languages
English (en)
Inventor
Attila PÜSKI
Original Assignee
Pueski Attila
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 Pueski Attila filed Critical Pueski Attila
Priority to AU48795/97A priority Critical patent/AU4879597A/en
Publication of WO1998017926A1 publication Critical patent/WO1998017926A1/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
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five 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
    • 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

Definitions

  • the present invention relates of a triple-shaft torque converter having a clutch drived by an engine, a drive shaft with drive gears placed in a gearbox casing which drive shaft joints to the said clutch, splined shafts holding releasable jointed gear's wheels and a differential in a differential casing.
  • the object of the present invention is to develop a simple and safety torque conver- ter device with the advantages of the known devices, like the short shafts and little space requirement, but simultaneously to eliminate the known disadvantages.
  • Present invention bases on the recognization that from view point both of the torque convert and the safety the binding point of the splined shaft with the differential is the best place for change an odd speed range to even one or vice versa.
  • An other recognization based on present invention is that the control means responsible for binding any intermediate wheel to differential ring and the control means responsible for the change of the instantly loaded shaft to the unloaded one, i.e. for the function-change among the two shaft preferably may be one and the same unit. Also an invention-based recognization is the idea, that mounting the splined shaft of odd gears separately from the splined shaft of even gears the speed change will be always on the instantly unloaded shaft meantime the driving bond between the running gear and the engine remains active with help of the other-, i.e. the loaded shaft. Consequently the device may realise with any more speed range distributed the odd and even gears in two separate splined shaft.
  • the drive shaft may mount to torque converter according to present invention also on the differential means' side because the arranging of the centre of the two intermediate wheels and of the drive shaft's end is near rectangular instead of right line.
  • a triple- shaft torque converter includes a clutch drived by an engine, a drive shaft with drive wheels placed in a gearbox casing which drive shaft joints to the said clutch, splined shafts holding releasable jointed gear's wheels, and a differential in a differential casing, further the odd splined shaft for the odd speed ranges and the even splined shaft for the even speed ranges and the reverse shaft with a reverse wheel, all arranged pa- rallel one to other and with the drive shaft, and preferably fitted with bearings in the gearbox casing where the splined shaft are conjoined to the differential ring with help of an engagement means operated by a shifter means.
  • the said torque converter preferably has an engagement means content of inter- mediate wheels fixable by synchro-cup switch operated by mechanical shifter.
  • An other preferably embodiment of the said converter has an engagement means content of intermediate wheels fixable by multi-plate clutches operated by mechanical or hydraulic shifter, as a hydraulic piston equipment.
  • the torque converter according to present invention preferably has an arrange wherein the geometrical sheet defined by the drive shaft and the odd splined shaft closes an angle different from 180° with the sheet defined by the even splined shaft and the drive shaft, which angle makes about 90°.
  • the above mentioned torque converter preferably may be characterized by that the shape and size of the wheels of 2 nd and 3 rd gear's are the same, and also of wheels of the 4 th and 5 th ones, wherein the tooth number of the odd and the even intermediate wheels are different.
  • Figure 1 A schematic representation of theoretical structure of the torque converter according to present invention.
  • Figure 2. The simplified view of a preferred embodiment with mechanical shifter.
  • Figure 3. A schematic section drawing of a preferred arrange of the drive shaft and the splined shafts.
  • FIG. 4 The simplified view of the embodiment having mechanical shifter with multiplate clutches.
  • Figure 5. A variation of device accordingly Fig.4. with hydraulic piston equipment instead of the mechanical shifter.
  • the torque converter defined with the sign 30 is arranged in the gearbox casing 1 1 and in the differential casing 12 mounted to it.
  • the main unites of the torque converter 30 according to present invention are two splined shaft 3, 5 arranged parallel one to other and both of them also with a drive shaft 4 and a reverse shaft.
  • the drive shaft 4 is driven from the engine 1 through the clutch 2.
  • the drive shaft is supplied with drive wheels 26 for the gears of different speed range, and the two splined shaft are provided with the gear's wheels, the odd splined shaft 3 has the wheels 13, 15, 17 of the odd gears, and the even splined shift 5 has the wheels 14, 16 of the even gears also the reverse wheel 18 of reverse gear.
  • the gear's wheels are releasable jointed to the splined shafts and may them fix to the shafts with synchro meshes 7, 8, 9.
  • parallel to the drive shaft 4 and between the drive shaft and even splined shaft lays the reverse shaft 6 of the reverse gear connected to the reverse wheel 18 with a connecting wheel 27.
  • the splined shafts lay in its bearings in the gearbox casing 11 and are extended into the differential casing 12 attached to the gearbox casing 11.
  • the differential ring 20 is connected to the odd splined shaft 3 with the help of odd intermediate wheel 19 or to the even splined shaft 5 with the help of even intermediate wheel 22.
  • Each said intermediate wheel is provided with a coupling 21 , 23, wherein an intermediate wheel and a coupling compose together an engagement means and the odd and the even engagement means are conjoined with a shifter 10 as shifter means and by this shifter 10 may control the conjoin of the differential ring 20 with the odd or even splined shaft 3, 5, by opening and closing the said coupling of the splined shaft just to be loaded.
  • the coupling means 21 , 23 are synchron-cup for closing and opening the conjoin of a splined shaft with its intermediate wheel, i.e. the conjoin of a splined shaft with the differential ring 20.
  • the drive shaft 4 driven by the engine 1 through the clutch 2 has a plurality of drive wheels 26 for moving the gear's wheels.
  • the drive shaft 4 has three gear's wheel, the first for first gear and reverse gear, the second for second and third gears, and the third for fourth and fifth gears.
  • each drive wheel 26 moves two gear's wheel, an odd and an even one.
  • the distance of the two splined shaft 3, 5 from the drive shaft 4 are equal, consequently the diameter of odd and even gear's wheels, moved by the one and the same drive wheel 26, are equal too.
  • the couplings 21 , 23 at the ends of both splined shaft 3, 5 are also completely the same, the difference that produce the ratio difference between the even and odd gears can be found only at the intermediate wheels 19, 22.
  • Customary the drive shaft 4 is produced together with the drive wheels 26 as cast in one unit.
  • the first gear's wheel 13 may be connected to the odd splined shaft 3 by the synchro mesh 7; the reverse gear is realized by the slide of the connecting wheel 27 situated on its short shaft 6 and the reverse gear's wheel 18 fixed on the even splined shaft 5, while the third gear's wheel 15 or the fifth gear's wheel 17 may be connected with the synchro mesh 8.
  • the second and fourth gears can be selected by the synchro mesh 9 using the second gear's wheel 14 or the fourth gear's wheel 16.
  • Each drive wheel 26 is always conjoined with one gear's wheel of odd splined shaft 3 and also with one wheel of even splined shaft 5 but only one of these two wheels is fixed to its splined shaft with the synchro mesh belongs to it.
  • Odd and even gears can be selected by means of the odd intermediate wheel 19 or the even intermediate wheel 22 laid out in the differential casing 12 at the ends of the odd splined shaft 3 and the even splined shaft 5, respectively.
  • Both intermediate wheels 19, 22 are always connected to the differential ring 20, but only one of them is fixed to its splined shaft 3, 5 by its coupling 21 , 23, wherein the couplings 21 , 23 are controlled, i.e. alternately established, by the shifter 10.
  • the first step is to change gear's wheel to a higher range with the item synchro mesh in the gear's wheel - drive wheel linkage on the (at that moment) idle spindled shaft and after shift the shifter 10 from one intermediate wheel to the other, thus setting on the torque converting function from one splined shaft to the other.
  • the operation of the torque converter 30 according to the present invention is accomplished that the power from the engine 1 and the clutch 2 gets to the drive shaft 4, from where it is transmitted by the connection of a drive wheel 26 and any gear's wheel to any splined shaft 3, 5 and through by the shifter 10 established coupling 21 , 23 and intermediate wheel 19, 22 lastly to the differential ring 20.
  • multi-plate clutches 24 substitute the synchron cups in the couplings 21 , 23.
  • the multi-plate clutchs 24 are mounted on the end of the splined shafts 3, 5.
  • the other parts of the construction of torque converter 30 are like to the above mentioned embodiments of present invention.
  • the shifter means controlled gear- shifting should be done by means of multi-plate clutches 24 for easy shift, because torque conversion does not cease during the shifting.
  • FIG.5. An other preferred embodiment of the present invention can be seen in Fig.5. wherein the shifter means of torque converter 30 is provided a hydraulic system instead of shifter 10 with hydraulic pistons 25 at both multi-plate clutch 24 likewise it is in use with traditional automatic epicyclic gear boxes.
  • the said hydraulic pistons 25 work with oil to actuate the said multi-plate clutchs 24 connecting to the odd intermediate wheel 19, or the even one 22 to own splinded shaft 3, ⁇ .
  • the connection between the odd intermediate gear 19 and the odd splined shaft 3 or between the even intermediate wheel 22 and the even splined shaft 5 is alternately established by means of the hydraulic pistons 25. Shifting between the two shaft can be done so, that the oil pressure arising on one piston terminates the oil pressure on the other one.
  • the odd intermediate wheel 19 is mounted on the odd splined shaft 3 and the even intermediate wheel 22 on the even splined shaft 5.
  • the version with the shifter 10, shown in the figure 2 is basically for use with an electric clutch.
  • the advantages of the torque converter 30 in accordance with the present invention are: a short, compact structure due to the triple-shaft solution, small dimensions; less torsion load due to the shorter shafts; a simple layshaft, the splined shaft of even and odd gears have identical dimensions, bearings; except for the first and reverse gears the gear's wheels opposite each other on the splined shafts, complete with the synchro mesh elements, are identical, irrespective of the number of gears realised; the couplings at the ends of both splined shaft are completely the same too, diffe- rence only can be found at the intermediate wheels, that produce the ratio difference between the even and odd gears; on the idle running splined shaft the next desired gear can be selected, the shaft is running idle, it requires a minimal synchronisation; on both splined shafts there can be one gear selected at the same time, because shifting is done by means of the coupling mechanisms of the odd and even gears, respectively; suddenly changing down several gears (2-3) is

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

Abstract

Transmission (30) qui comporte un arbre d'entrée (4) entraîné par un moteur (1) par l'intermédiaire d'un embrayage (2). Deux contre-arbres (3, 5) portent des roues d'engrenage (13, 14, 15, 16, 17) libérables et alternativement entraînent un engrenage d'entrée (20) différentiel à l'aide d'engrenages (19, 22) connectés aux contre-arbres (3, 5) par des mécanismes de couplage (21, 23). L'arbre d'entrée (4) et les contre-arbres (3, 5) sont parallèles les uns aux autres.
PCT/HU1997/000065 1996-10-21 1997-10-17 Transmission a deux contre-arbres WO1998017926A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU48795/97A AU4879597A (en) 1996-10-21 1997-10-17 Double countershaft transmission

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
HU9602903A HUP9602903A3 (en) 1996-10-21 1996-10-21 Gear with three shafts
HUP9602903 1996-10-21

Publications (1)

Publication Number Publication Date
WO1998017926A1 true WO1998017926A1 (fr) 1998-04-30

Family

ID=89994373

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/HU1997/000065 WO1998017926A1 (fr) 1996-10-21 1997-10-17 Transmission a deux contre-arbres

Country Status (3)

Country Link
AU (1) AU4879597A (fr)
HU (1) HUP9602903A3 (fr)
WO (1) WO1998017926A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2837251A1 (fr) * 2002-03-13 2003-09-19 Luk Lamellen & Kupplungsbau Transmission et, plus particulierement, transmission a double embrayage
CN100575742C (zh) * 2004-11-23 2009-12-30 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 机动车辆的有级式变速装置
WO2010066313A1 (fr) * 2008-12-08 2010-06-17 Gm Global Technology Operations, Inc. Transmission à double embrayage
US8661925B2 (en) 2007-04-30 2014-03-04 Parker Hannifin Corporation Hydraulically operated shifter for power take-off
WO2014042575A1 (fr) * 2012-09-11 2014-03-20 Scania Cv Ab Système de transmission d'un véhicule à moteur

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3078673A (en) 1960-05-27 1963-02-26 Deere & Co Hydraulic control system for transmission and the like
DE3546454A1 (de) 1985-08-22 1987-02-26 Porsche Ag Gangschaltgetriebe fuer ein kraftfahrzeug mit doppelkupplung
US5357821A (en) * 1993-04-13 1994-10-25 General Motors Corporation Transmission and shift control

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3078673A (en) 1960-05-27 1963-02-26 Deere & Co Hydraulic control system for transmission and the like
DE3546454A1 (de) 1985-08-22 1987-02-26 Porsche Ag Gangschaltgetriebe fuer ein kraftfahrzeug mit doppelkupplung
US5357821A (en) * 1993-04-13 1994-10-25 General Motors Corporation Transmission and shift control

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2837251A1 (fr) * 2002-03-13 2003-09-19 Luk Lamellen & Kupplungsbau Transmission et, plus particulierement, transmission a double embrayage
WO2003078864A1 (fr) * 2002-03-13 2003-09-25 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Boite de vitesses, notamment boite de vitesses a embrayage double
CN100575742C (zh) * 2004-11-23 2009-12-30 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 机动车辆的有级式变速装置
US8661925B2 (en) 2007-04-30 2014-03-04 Parker Hannifin Corporation Hydraulically operated shifter for power take-off
WO2010066313A1 (fr) * 2008-12-08 2010-06-17 Gm Global Technology Operations, Inc. Transmission à double embrayage
WO2014042575A1 (fr) * 2012-09-11 2014-03-20 Scania Cv Ab Système de transmission d'un véhicule à moteur
EP2895770A4 (fr) * 2012-09-11 2016-11-30 Scania Cv Ab Système de transmission d'un véhicule à moteur
KR101741197B1 (ko) * 2012-09-11 2017-05-29 스카니아 씨브이 악티에볼라그 자동차용 변속 시스템
US9772016B2 (en) 2012-09-11 2017-09-26 Scania Cv Ab Transmission system for a motor vehicle

Also Published As

Publication number Publication date
HUP9602903A3 (en) 2000-03-28
HU9602903D0 (en) 1996-12-30
HUP9602903A2 (hu) 1998-09-28
AU4879597A (en) 1998-05-15

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