GB2465853A - A double clutch transmission - Google Patents

A double clutch transmission Download PDF

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Publication number
GB2465853A
GB2465853A GB0822794A GB0822794A GB2465853A GB 2465853 A GB2465853 A GB 2465853A GB 0822794 A GB0822794 A GB 0822794A GB 0822794 A GB0822794 A GB 0822794A GB 2465853 A GB2465853 A GB 2465853A
Authority
GB
United Kingdom
Prior art keywords
double
clutch transmission
input shaft
clutch
layshaft
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Withdrawn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
GB0822794A
Other versions
GB0822794D0 (en
Inventor
Eckhard Kirchner
Mikael Westerberg
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.)
GM Global Technology Operations LLC
Original Assignee
GM Global Technology Operations LLC
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 GM Global Technology Operations LLC filed Critical GM Global Technology Operations LLC
Priority to GB0822794A priority Critical patent/GB2465853A/en
Publication of GB0822794D0 publication Critical patent/GB0822794D0/en
Priority to PCT/EP2009/007427 priority patent/WO2010066313A1/en
Publication of GB2465853A publication Critical patent/GB2465853A/en
Withdrawn legal-status Critical Current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
    • F16H3/006—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
    • 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
    • F16H3/10—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 one or more one-way clutches as an essential feature

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

Abstract

A double-clutch transmission comprises an input shaft 1, an output shaft and at least two alternative paths for transmitting torque from the input shaft 1 to the output shaft. Each of the alternative paths comprises a layshaft 10,13 and a friction clutch 19, 21, 20, 22 for selectively enabling or disabling torque flow along the path located on that layshaft 10, 13.

Description

Double Clutch Transmission
Description
Double clutch transmissions have been the subject of considerable public interest in recent times due to the capability to shift gears without interrupting torque flow. This allows for very smooth shifting operations which are hardly perceptible for the passengers of a motor vehicle.
Generally, conventional double clutch transmissions comprise an input shaft formed of at least two parts, a solid shaft member and a hollow shaft member extending along part of the solid shaft member and being rotatable with respect to the latter, both shaft members carrying a plurality of drive gearwheels that mesh with driven gearwheels on one or more layshafts, and each shaft member has a friction clutch associated to it for selectively enabling or disabling torque transmission from an engine to the shaft member.
In such a conventional double clutch transmission, the two friction clutches are arranged one behind the other in the axial direction of the input shaft, thus contributing significantly to the overall length of the transmission. In another prior art design, clutches are coaxially nested. Since in this design dimensions of the clutches are different, their load-bearing capacities tend to be ditterent, too.
The object of the present invention is to provide a double clutch transmission which is suitable for a particularly compact design.
The object is achieved by a double clutch transmission comprising an input shaft, an output shaft and at least two alternative paths for transmitting torque from the input shaft to the output shaft, each of the alternative paths comprising a friction clutch for selectively enabling or disabling torque flow along said path, in which each path comprises a layshaft and the friction clutch associated to a given path is located on the layshaft of said path. In such a transmission, instead of placing the two clutches one behind the other in the axial direction or nesting them radially, as conventional, they can be placed one beside the other, so that the overall length of the transmission can be reduced. If the diameter of the two clutches is not larger than that of the largest gearwheel on their respective layshaft, the lateral dimensions of a transmission are not increased by placing the friction clutches on the layshafts.
In most practical cases, there will be two or more driven gearwheels on each layshaft, meshing with drive gearwheels of the input shaft. In order for the friction clutch to be able to interrupt torque flow via its associated layshaft, no matter which gearwheels are currently under load, a friction clutch of the given path should be arranged to enable or disable torque flow from the layshaft associated to that path to the output shaft.
To this effect, each friction clutch preferably has a first member flOiL LuLdLbiy inouncea on its associated layshaft, and a sleeve carried by said layshaft has a second member of said friction clutch and an output pinion non-rotatably mounted on it.
The output pinions of the two layshafts preferably mesh with a same gear element on the output shaft. The output shaft can be front or rear drive shaft or a propeller shaft, so that the gearbox of the invention can be used in front wheel drive, rear wheel drive or all wheel drive vehicles. The said gear element can be a differential. In an all-wheel drive vehicle, the gear element preferably is a front-rear torque distribution unit. For rear wheel driven applications the output shaft can be arranged coaxially to the crankshaft as well with a given off-set.
In order to facilitate access to the friction clutches for maintenance or repair purposes, it is useful if the friction clutches are located at a side of the transmission, or, more precisely, on each layshaft the output pinion is placed between the friction clutch and at least one of the driven gearwheels.
Preferably, the first path comprises odd-numbered forward gears, and the second path comprises even-numbered forward gears. In this way, shifting between adjacent gears is possible by opening one of the friction clutches and simultaneously closing the other, so that the flow of torque is not interrupted during shifting.
A reverse gear is preferably incorporated into the second path. In this way, shifting between first forward and reverse gears becomes possible by simply opening one friction clutch and closing the other.
Since tho omount of tha tauuhi5ion ratios ot first forward and reverse gears usually is rather similar, it is convenient that a forward gear and the reverse gear should share a drive gearwheel on the input shaft.
For instance, one drive gearwheel may mesh directly with two other gearwheels, namely a forward driven gearwheel on one of the output shafts, preferably the driven gearwheel of the first gear, and a reversing gearwheel on an auxiliary shaft, which in turn meshes with the driven gearwheel of the reverse gear on the other output shaft.
Alternatively, there can be a driven gearwheel on one output shaft which meshes with an associated drive gearwheel on the input shaft and with the reverse driven gearwheel on the other output shaft.
Since the torque transmitted in the first forward gear can be higher than in higher forward gears, the drive gearwheel shared by first forward and reverse gears is best placed closer to a torque receiving end of the input shaft than all other drive gearwheels.
Similarly, the driven gearwheels on the two layshafts associated to first forward and reverse gears are preferably closer to the friction clutches than any other driven gearwheels.
In order to achieve a convenient spacing between the gear ratios of the various forward gears, it is convenient for the second forward gear to have a drive gearwheel on the input shaft exclusively dedicated to it, in particular, if the total number of forward gears is even.
In order to achieve flexible gear ratios of the different gears, the two pinions on the layshaft may have different diameters. Also the distances between the input shaft and the two layshafts may be different.
A torsion damper may be provided in the input shaft in order to prevent clattering of meshing gearwheels due to speed variations of an engine driving the input shaft.
For preventing unwanted reverse movement of the vehicle, in particular when driving uphill, a shiftable one-way clutch may be associated to at least one of the layshafts.
The one-way clutch preferably has blocking elements which are rotatable around the layshaft and have an unbiocking position radially outward of a blocking position, so that when the blocking elements rotate, they are urged towards the unbiocking position by centrifugal force. In this way, the one-way clutch is automatically disengaged if the vehicle speed is above a predetermined limit. Alternatively, other one-way clutch concepts without blocker bodies such as other friction based concepts, form-or force fit units may be used.
In a vehicle comprising the double clutch transmission as described above, the power train may be simplified by providing a rigid connection between a motor and the input shaft of the double clutch transmission. In such an arrangement the reflected inertia of the driven gears to the input shaft shall be evenly distributed to reduce clatter sensitivity.
Further features and advantages of the invention 1 -.._._-_-.._L. ._1._._..._....i_ WiLL. L)tL.L.flhI}JpaL11L.LLL'lLL L1L �JJ.
embodiments thereof referring to the appended drawings.
Figs. 1 to 5 are schematic diagrams of double clutch transmissions according to first to fifth embodiments of the invention.
The transmission shown in Fig. 1 has an input shaft 1 which is permanently connected to the crankshaft of a motor 2. The input shaft 1 carries a torsion damper, e.g. a double-mass flywheel 3. Drive gearwheels 4 to 7 are splined to input shaft 1. The diameter of the drive gearwheels increases with their distance from motor 2.
The smallest drive gearwheel 4, closest to motor 2, meshes with a driven gearwheel 9 on a layshaft 10, and with a reversing gearwheel 11, which, in turn, meshes with a driven gearwheel 12 on a second layshaft 13.
Second smallest drive gearwheel 5 meshes only with a driven gearwheel 14 on second layshaft 13. The two largest drive gearwheels 6, 7 mesh with driven gearwheels 15, 16 and 17, 18, respectively, on first and second layshafts 10, 13.
The transmission comprises two friction clutches, one on each layshaft 10, 13. The friction clutches may be of the wet or the dry type, as load requires and available package size permits. Each friction clutch has an upstream member 19, 20 comprising a plurality of discs splined to its respective layshaft 10, 13, and a downstream member 21, 22 formed of a plurality of discs connected to a sleeve 23, 24 rotatably mounted on shaft 10, 13. In a space between each friction clutch and a facing driven gearwheel 9, 12, an output pinion 25, 26 is mounted on sleeve 23, 24. The two output pinions 25, 26 mesh with a same diLLLeI1Lia1, not shown.
A dog clutch, not shown, is associated to each drive gearwheel 4, 5, 6 and 7, in order to selectively lock one of them at a time to input shaft 1.
The transmission of Fig. 1 has six forward gears and a reverse gear. Since the distance dl between input shaft 1 and layshaft 10 is greater than the distance d2 between input shaft 1 and layshaft 13, among the two gears formed e.g. by gearwheels 7, 17, 18, the one formed by gearwheels 7 and 18 is the higher one. Given the size relations of the gearwheels shown in Fig. 1, it is readily apparent that gearwheels 7, 18 form the sixth gear, gearwheels 7, 17 form the fifth gear, gearwheels 6, 16 form the fourth gear, and gearwheels 6, 15 form the third gear. Among the gear ratios of these four gears, three can be set arbitrarily by choosing the distances dl, d2 between the shafts 1, 10, 13 and the diameters of e.g. gearwheels 6, 7. The diameters of gearwheels 15-18 are determined by these choices, so that a fourth gear ratio is predetermined by the geometrical constraints. If first and second gear shared a drive gearwheel, it would not be possible to choose their gear ratios independently from one another. By instead using dedicated drive gearwheel 5 only for the second gear, the transmission ratio of this gear can be set arbitrarily. Since d2 is smaller than dl, gearwheel 12 must be smaller than gearwheel 9, and the amount of the gear ratio of the reverse gear can only be smaller than that of the first gear.
Geometrical constraints concerning the amount of the transmission ratio of the reverse gear can be relieved by providing not a single reversing gearwheel 11 as shown in Fig. 1, but stepped reversing gearwheels 27, fS r.__ _ * J_1__,.__ 11UWLi ill � .L. .. y IIV.L11 L1I LLLJL Lfl1, . I U.L the two reversing gearwheels 27 28 mesh with drive gearwheel 4 and the smaller one, 28, with driven gearwheel 9, the amount of the transmission ratio of the reverse gear can be increased beyond what the geometrical constraints would allow in the embodiment of Fig. 1.
Fig. 3 is a diagram of a seven-gear transmission according to the invention. Components common to this embodiment and the previous ones have identical reference numerals and are not described again. An additional driven gearwheel 29 is provided on layshaft 10, meshing with the second smallest drive gearwheel 5. Here the distance d2 between layshaft 13 and input shaft 1 is larger than the distance dl between layshaft 10 and input shaft 1. Therefore, gearwheel pairs 5 + 27, 6 + 15 and 7 + 17 give third, fifth and seventh gears, respectively, whereas gearwheel pairs 5 + 14, 6 + 16 and 7 + 18 combine to form gears 2, 4 and 6, as in the previous embodiments.
Due to the increased distance d2 between shafts 1 and 13, gearwheel 12 need not be smaller than gearwheel 9, so that the amount of the transmission ratio of the reverse gear is not necessarily smaller than that of the first gear if a single reversing gearwheel 11 meshing with gearwheels 4, 12 is used.
Fig. 4 illustrates a six-gear transmission which is similar to that of Fig. 1 except for the presence of a one-way clutch 30 in sleeve 24. In a way familiar to the man of the art, one way clutch 30 has concentrical inner and outer races and a plurality of blocking elements 31 in a space between the two races, which are movably connected to one of the races to engage steps formed at the other race, whereby a rotation of the two races with respect to each other in a prohibited direction is blocked. In the one way clutch 30 of Fig. 4, the outer race has the biukixiy elements 30 connected to it and rotates with sleeve 24, whereas the inner race is solidly connected to a casing of the transmission. While a forward gear is engaged in the transmission, the blocking elements 30 are freely movable, so that they come to engage the steps of the inner race if the differential rotates in a reverse direction, preventing the vehicle from rolling backwards if no gear is engaged. The blocking elements 31 are connected to a gearshift lever, not shown, in order to be blocked in a position adjacent to the outer race if the reverse gear is selected, in order to prevent them from blocking in that case. If the vehicle is rolling forward above a predetermined speed, the blocking elements 31 rotate with sleeve 24 and are urged into that same position adjacent to the outer race by centrifugal force. Thus there is no contact between them and the inner race, and, hence, no wear, when the vehicle is being driven at a speed of more than a few kilometres per hour.
The transmission of Fig. 5 differs from that off Fig. 1 by the fact that there is no reversing gearwheel 11 on an auxiliary shaft, so that drive gearwheel 4 meshes only with driven gearwheel 9 on layshaft 10.
Gearwheel 9, in turn, meshes with gearwheel 12 on layshaft 13, causing the latter to run in the reverse direction.
List of reference signs 1 input shaft 2 motor 3 double-mass flywheel 4 drive gearwheel drive gearwheel 6 drive gearwheel 7 drive gearwheel 8 9 driven gearwheel layshaft 11 reversing gearwheel 12 driven gearwheel 13 second layshaft 14 driven gearwheel driven gearwheel 16 driven gearwheel 17 driven gearwheel 18 driven gearwheel 19 friction clutch/upstream member friction clutch/upstream member 21 friction clutch/downstream member 22 friction clutch/downstream member 23 sleeve 24 sleeve output pinion 26 output pinion 27 driven gearwheel 28 reversing gearwheel 29 reversing gearwheel one-way clutch 31 blocking elements

Claims (15)

  1. Claims 1. A double-clutch transmission comprising an input shaft (1), an output shaft and at least two alternative paths for transmitting torque from the input shaft (1) to the output shaft, each of the alternative paths comprising a friction clutch (19, 21; 20, 22) for selectively enabling or disabling torque flow along said path, characterized in that each path comprises a layshaft (10; 13) and that the friction clutch (19, 21; 20, 22) associated to a given path is located on the layshaft (10; 13) of said path.
  2. 2. The double-clutch transmission of claim 1, wherein the friction clutch (19, 21; 20, 22) of a given path is arranged to enable or disable torque flow from the layshaft (10; 13) associated to that path to the output shaft.
  3. 3. The double-clutch transmission of claim 2, wherein each friction clutch (19, 21; 20, 22) has a first member (19; 20) non-rotatably mounted on its associated layshaft (10; 13) and that a sleeve (23; 24) carried by said layshaft (10; 13) has a second member (20; 22) of said friction clutch and an output pinion (25; 26) non-rotatably mounted on it.
  4. 4. The double-clutch transmission of claim 3, wherein the output pinions (25; 26) of said two layshafts (10; 13) mesh with a differential of the output shaft.
  5. 5. The double-clutch transmission of claim 3 or 4, wherein on each layshaft (10; 13) the output pinion (25; 26) is placed between the friction clutch (19, 21; 20, 22) and at least one gearwheel (9; 12; 14- 18) which mc3has with a geaLwiil (4-7) of the input shaft (1).
  6. 6. The double-clutch transmission of any of the preceding claims, wherein the first path comprises odd-numbered forward gear ratios, and the second path comprises even-numbered gear ratios.
  7. 7. The double-clutch transmission of claim 6, wherein the second path further comprises a reverse gear.
  8. 8. The double-clutch transmission of claim 6 or 7, wherein first forward gear and reverse gear share a drive gearwheel (4) on the input shaft (1)
  9. 9. The double-clutch transmission of claim 8, wherein among all drive gearwheels (4-7) of the input shaft (1), the drive gearwheel (4) shared by first forward and reverse gears is closest to a torque-receiving end of the input shaft (1)
  10. 10. The double-clutch transmission of claim 8 or 9, wherein driven gearwheels (9; 12) on said two layshafts (10; 13) associated to said first forward and reverse gears are closer to the friction clutches (19, 21; 20, 22)than any other driven gearwheels.
  11. 11. The double-clutch transmission of any of claims 6 to 10, wherein the total number of forward gears is even, and the second forward gear has a drive gearwheel (5) on the input shaft (1) exclusively dedicated to it.
  12. 12. The double-clutch transmission of any of the preceding claims, wherein a torsion damper (3) is provided in the input shaft (1).
  13. 13. The double-clutch transmission of any of the preceding claims, wherein at least one of the layshafts (13) has a one-way clutch (30) associated to it.
  14. 14. The double-clutch transmission of claim 13, wherein blocking elements (31) of the one-way clutch (30) are rotatable around the layshaft (13), and an unbiocking position of the blocking elements (31) is radially outward of a blocking position.
  15. 15. A motor vehicle in which a motor (2) is permanently connected to the input shaft (1) of a double-clutch transmission according to any of the preceding claims.
GB0822794A 2008-12-08 2008-12-08 A double clutch transmission Withdrawn GB2465853A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
GB0822794A GB2465853A (en) 2008-12-08 2008-12-08 A double clutch transmission
PCT/EP2009/007427 WO2010066313A1 (en) 2008-12-08 2009-10-16 Double clutch transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB0822794A GB2465853A (en) 2008-12-08 2008-12-08 A double clutch transmission

Publications (2)

Publication Number Publication Date
GB0822794D0 GB0822794D0 (en) 2009-01-21
GB2465853A true GB2465853A (en) 2010-06-09

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
GB0822794A Withdrawn GB2465853A (en) 2008-12-08 2008-12-08 A double clutch transmission

Country Status (2)

Country Link
GB (1) GB2465853A (en)
WO (1) WO2010066313A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011114928A1 (en) 2011-10-06 2013-04-11 Lufthansa Technik Ag Combustion chamber for a gas turbine
CZ303794B6 (en) * 2007-03-08 2013-05-09 Sew Eurodrive Cz S. R. O. Multiple-speed gearbox with branching of transmitted load
CZ303858B6 (en) * 2012-05-11 2013-05-29 Zetor Tractors A.S. Arrangement of two-flow reversing transmission, especially for motor vehicles and construction machinery, with two branches of power flow

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105179610A (en) * 2015-06-08 2015-12-23 北京航天动力研究所 Automatic speed change mechanism which is driven by single motor and has high speed and low speed switching function
CN105202127B (en) * 2015-11-11 2018-05-08 重庆青山工业有限责任公司 A kind of double-clutch automatic gearbox

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19939334A1 (en) * 1999-08-19 2001-03-08 Daimler Chrysler Ag Method for shifting double-clutch gearbox without tractive force interruption has two lay shafts connected to output shaft through shiftable gear stages and associated with friction clutch for connection to drive motor
WO2005012762A1 (en) * 2003-08-01 2005-02-10 Daimlerchrysler Ag Twin clutch transmission with coaxial drive and output
US20060117882A1 (en) * 2003-06-06 2006-06-08 Carsten Gitt Twin-clutch transmission
US20080047379A1 (en) * 2006-08-23 2008-02-28 Borgerson James B Powertrain With Torque Converter And Axially Compact Seven Speed Dual Clutch Transmission

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE448359B (en) * 1985-07-01 1987-02-16 Volvo Ab MOTORFORDONSVEXELLADA
DE3621545A1 (en) * 1986-06-27 1988-01-28 Tropp Axel Dipl Ing Fh Double clutch gear box for vehicles - has gear levels divided between two input shafts selectable by separate clutch units
HUP9602903A3 (en) * 1996-10-21 2000-03-28 Pueski Attila Gear with three shafts
EP1124079A3 (en) * 2000-01-22 2006-08-09 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Six speed vehicle transmission

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19939334A1 (en) * 1999-08-19 2001-03-08 Daimler Chrysler Ag Method for shifting double-clutch gearbox without tractive force interruption has two lay shafts connected to output shaft through shiftable gear stages and associated with friction clutch for connection to drive motor
US20060117882A1 (en) * 2003-06-06 2006-06-08 Carsten Gitt Twin-clutch transmission
WO2005012762A1 (en) * 2003-08-01 2005-02-10 Daimlerchrysler Ag Twin clutch transmission with coaxial drive and output
US20080047379A1 (en) * 2006-08-23 2008-02-28 Borgerson James B Powertrain With Torque Converter And Axially Compact Seven Speed Dual Clutch Transmission

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CZ303794B6 (en) * 2007-03-08 2013-05-09 Sew Eurodrive Cz S. R. O. Multiple-speed gearbox with branching of transmitted load
DE102011114928A1 (en) 2011-10-06 2013-04-11 Lufthansa Technik Ag Combustion chamber for a gas turbine
WO2013050105A1 (en) 2011-10-06 2013-04-11 Lufthansa Technik Ag Combustion chamber for a gas turbine
CZ303858B6 (en) * 2012-05-11 2013-05-29 Zetor Tractors A.S. Arrangement of two-flow reversing transmission, especially for motor vehicles and construction machinery, with two branches of power flow

Also Published As

Publication number Publication date
GB0822794D0 (en) 2009-01-21
WO2010066313A1 (en) 2010-06-17

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