CN103511614A - Dual clutch transmission and method for shifting a dual clutch transmission - Google Patents
Dual clutch transmission and method for shifting a dual clutch transmission Download PDFInfo
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- CN103511614A CN103511614A CN201310232728.2A CN201310232728A CN103511614A CN 103511614 A CN103511614 A CN 103511614A CN 201310232728 A CN201310232728 A CN 201310232728A CN 103511614 A CN103511614 A CN 103511614A
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 255
- 238000000034 method Methods 0.000 title claims description 27
- 230000009977 dual effect Effects 0.000 title description 15
- 230000008878 coupling Effects 0.000 claims description 67
- 238000010168 coupling process Methods 0.000 claims description 67
- 238000005859 coupling reaction Methods 0.000 claims description 67
- 230000001360 synchronised effect Effects 0.000 claims description 65
- 230000006978 adaptation Effects 0.000 claims description 8
- 238000006386 neutralization reaction Methods 0.000 claims description 2
- 230000007935 neutral effect Effects 0.000 description 17
- 238000012163 sequencing technique Methods 0.000 description 4
- 230000035939 shock Effects 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000008676 import Effects 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- 241000446313 Lamella Species 0.000 description 1
- 238000005056 compaction Methods 0.000 description 1
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- 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
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- 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
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- 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
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- 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
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- 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
- F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Arrangement Of Transmissions (AREA)
Abstract
The invention relates to a double clutch transmission, which is provided with: a first transmission input shaft which can be connected to the first sub-transmission, a second transmission input shaft which can be connected to the second sub-transmission, a primary shaft which can be connected to a drive shaft of a motor vehicle engine, and a secondary shaft which can be coupled to the primary shaft by means of a slip clutch, wherein either the primary shaft can be coupled to the first transmission input shaft or to the second transmission input shaft via an unsynchronized form-fit clutch and the secondary shaft can be coupled to the first transmission input shaft or to the second transmission input shaft via a synchronizable form-fit clutch, alternatively, the secondary shaft can be coupled to the first transmission input shaft or to the second transmission input shaft via an unsynchronized form-fit clutch and the primary shaft can be coupled to the first transmission input shaft or to the second transmission input shaft via a synchronizable form-fit clutch.
Description
Technical field
The present invention relates to a kind of dual-clutch transmission and a kind of method for switch dual clutch speed-changer, by means of them, can substantially not interrupt tractive force and carry out the switching of vehicle transmission.
Background technique
By the known a kind of dual-clutch transmission of DE 10 2,004 041 525 A1, have: first transmission input shaft that can be connected with the first sub-speed changer and second transmission input shaft that can be connected with the second sub-speed changer with respect to the coaxial heart of the first transmission input shaft, wherein, the second transmission input shaft axially staggers and arranges with respect to the first transmission input shaft.These transmission input shafts are configured to hollow shaft, through the live axle of these hollow shaft guiding motor car engines.This live axle can be respectively by being coupled by means of the synchronous jaw clutch of synchronizing ring and the first transmission input shaft and the second transmission input shaft.By slippage clutch (Rutschkupplung), can make a bridge joint axle radially staggering with respect to the first transmission input shaft and live axle coupling upper, this bridge joint axle and the middle hollow shaft tooth engagement of arranging with the coaxial heart of these transmission input shafts between the first transmission input shaft and the second transmission input shaft in the axial direction.In the situation that the bridge joint axle in coupling, middle hollow shaft can be respectively by being coupled by means of the synchronous jaw clutch of synchronizing ring and transmission input shaft, live axle and this transmission input shaft are not just in time coupled, to prepare substantially not interrupt tractive force ground gear shift.Thus, the part that always becomes larger of power stream is delivered to the transmission input shaft of the new shelves of hanging by bridge joint axle and middle hollow shaft from live axle, until by live axle can be synchronous jaw clutch substantially no longer realize power and flow.After this, can open this jaw clutch, and, can by means of another can synchronous jaw clutch make live axle with newly hang into the other transmission input shaft coupling of shelves, after this, can open in the middle of hollow shaft can be synchronous jaw clutch and slippage clutch.Guarantee thus, at live axle in time of a coupling directly and in transmission input shaft, also the power that can realize between live axle and the transmission output shaft of dual-clutch transmission by the bridge joint axle on can being coupled and middle hollow shaft flows, to can realize the shelves that substantially do not interrupt tractive force ground switch dual clutch speed-changer.
Existence can realize the advantageously lasting demand of switch dual clutch speed-changer of simple and cost.
Summary of the invention
Task of the present invention is, realizes a kind of dual-clutch transmission and a kind of method for switch dual clutch speed-changer, wherein, can be simply and cost advantageously carry out the switching of dual-clutch transmission.
The solution of this task according to the present invention by a kind of dual-clutch transmission with claim 1 feature, a kind of have claim 8 feature, for the method for switch dual clutch speed-changer, claim 9 feature, for the method for switch dual clutch speed-changer, a kind of have claim 10 feature, for the method for switch dual clutch speed-changer and a kind of have claim 11 feature, for the method for switch dual clutch speed-changer, realize.Preferred configuration of the present invention provides in the dependent claims, and these dependent claims can represent respectively object of the present invention either alone or in combination.
According to the present invention, in order substantially not interrupt the speed changer shelves of tractive force ground switching machine motor-car, be provided with: first transmission input shaft that can be connected with the first sub-speed changer, for engine torque being imported to this first sub-speed changer; One second transmission input shaft that can be connected with the second sub-speed changer, for importing to engine torque this second sub-speed changer; The one elementary axle that can be connected with the live axle of motor car engine, can be by a clutch that can skid, secondary axle that especially friction clutch and described elementary axle are coupled, the engine torque being entered by this elementary spindle guide for branch for engine torque being imported to described dual-clutch transmission neutralization one; Wherein, or described elementary axle can be by the sealed clutch of a nonsynchronous shape, especially there is no the jaw clutch of synchronizing ring, with described the first transmission input shaft or with described the second transmission input shaft, be coupled, and, in order to make this elementary axle and corresponding another transmission input shaft synchronizing, described secondary axle can by one can be synchronous the sealed clutch of shape, especially there is the jaw clutch of synchronizing ring, with described the first transmission input shaft or with described the second transmission input shaft coupling; Or described secondary axle can be by the sealed clutch of a nonsynchronous shape, especially there is no the jaw clutch of synchronizing ring, with described the first transmission input shaft or with described the second transmission input shaft, be coupled, and, in order to make this secondary axle and corresponding another transmission input shaft synchronizing, described elementary axle can by one can be synchronous the sealed clutch of shape, especially there is the jaw clutch of synchronizing ring, with described the first transmission input shaft or with described the second transmission input shaft coupling.
The clutch that can skid by means of this and this can be synchronous the sealed clutch of shape, also can realize the synchronizing for the sealed clutch of nonsynchronous shape, thereby for the synchronized other structural element respectively for the sealed clutch of nonsynchronous shape, especially synchronizing ring is unwanted.By save synchronizing ring can be simply and cost advantageously carry out the switching of dual-clutch transmission.
Normally, travel in service, preferably by the sealed clutch of nonsynchronous shape, realize power and flow.For gear shift, can be in the sub-speed changer of another not load of correspondence new shelves of preliminary election and making on another corresponding transmission input shaft is coupled in this sub-speed changer, thereby this transmission input shaft can together rotate.Substantially the transmission input shaft that not load ground together rotates can especially with to this time point also be synchronizeed and be coupled in static secondary axle by sealed clutch by means of shape that can be synchronous.The clutch that can skid by closure, can make power stream by secondary axle and the sealed clutch deflection of shape that can be synchronous, thereby can make power stream substantially decline until zero by the transmission input shaft of the sealed clutch of nonsynchronous shape and old shelves.Then, can open without problems the sealed clutch of nonsynchronous shape, thus the transmission input shaft that makes old shelves only also substantially not load ground together rotate and can decoupling zero in the sub-speed changer of correspondence.Because elementary axle substantially no longer provides pull-up torque (Schleppmoment), the slippage of the clutch that can skid can reduce, until elementary axle and secondary axle are substantially with identical rotational speed.Thus, the sealed clutch of shape and the sealed clutch of nonsynchronous shape that can be synchronous also rotate with same rotational speed, thereby the sealed clutch of nonsynchronous shape is automatically synchronizeed with the transmission input shaft of new shelves, and do not need measure other, that synchronize with the transmission input shaft of new shelves.The sealed clutch of nonsynchronous shape can be coupled with the transmission input shaft of new shelves without problems, and thus, power stream can be realized by the sealed clutch of nonsynchronous shape again completely.For this reason, the clutch that can open the sealed clutch of synchronous shape and can skid, thus finish gear shift.For gear shift subsequently, can again carry out pre-gear selecting and carry out gear shift by means of the sealed clutch of synchronous shape and the clutch that can skid, until can regenerate the operation of normally travelling with power stream by the sealed clutch of nonsynchronous shape.
By travel normally in service by elementary axle be attached to power this elementary axle, the sealed clutch of nonsynchronous shape and flow, the live axle that can make motor car engine is coupled by the output shaft of few especially intermediary element and motor car engine, thereby avoids loss in efficiency.Alternatively likely, normally travel operating power stream by secondary axle and be attached in this case this secondary axle, the sealed clutch of nonsynchronous shape realizes.In this case, the sealed clutch of shape that can be synchronous can be attached to elementary axle.Thus, normally travelling in servicely, power stream can be realized by clutch closure, that can skid.This makes it possible to filter out that cause, unexpected, the less desirable torque shock ends (" shock ") by the clutch that can skid, its mode is, it is in service and prevent from transmitting less desirable torque shock ends that more than that limit, maximum nominal torque, this clutch that can skid enters into slippage.Can improve driving comfort thus.Under this alternative case, if power stream is realized by the transmission input shaft of new shelves by means of the sealed clutch of shape that can be synchronous substantially, when gear shift, make the clutch that can skid open, to the sealed clutch of nonsynchronous shape is opened and separated with the transmission input shaft of old shelves.After this, can be the again closed clutch that can skid, and after the rotating speed of elementary axle and the rotating speed of secondary axle are suitable, can the sealed clutch of closed nonsynchronous shape and open can be synchronous the sealed clutch of shape.
For example can in the first sub-speed changer, by means of the first transmission input shaft, connect the speed changer shelves of odd number, for example first grade, third gear and the 5th grade, and can be by means of the speed changer shelves of the second transmission input shaft connection even number in the second sub-speed changer, for example second gear, fourth speed and the 6th grade, or conversely.For this reason, especially can by means of can synchronous sliding sleeve make corresponding transmission input shaft and be attached to corresponding shelves, in corresponding transmission input shaft and the gears of the gear pair between a transmission output shaft especially.Transmission output shaft especially can be coupled by gear correspondence, that consist of attached troops to a unit gear pair and the first transmission input shaft and the second transmission input shaft.The first sub-speed changer and the second sub-speed changer can be arranged in common case of transmission.Especially, each speed changer shelves of the first sub-speed changer and each speed changer shelves of the second sub-speed changer are arranged on ground, front and back in the axial direction, wherein, for example likely, first all speed changer shelves of one sub-speed changer are set, then all speed changer shelves of another sub-speed changer are set in the axial direction.
Elementary axle can be directly or indirectly with the live axle of motor car engine, especially bent axle is connected.On elementary axle for example can be by torsional vibration damper, especially double mass flywheel is coupled on live axle.The clutch that can skid can be connected with elementary axle without relative rotation with input side.In order to import torque, secondary axle is only connected with elementary axle by the clutch that can skid indirectly.The clutch that can skid for example can be configured as especially torque converter that can bridge joint, and wherein, the clutch that can skid is especially configured as friction clutch, for example plate clutch or lamella clutch.Friction clutch can have pressing plate, and this is coupled with elementary axle without relative rotation to pressing plate, and the power stage element that is clutch disk form of the clutch that can skid can be coupled with secondary axle without relative rotation.By means of one can be by operation system with respect to this to the axially movable pressure strip of pressing plate, clutch disk friction can be pressed in locking manner between pressing plate and pressure strip, so that closed friction clutch.Especially can be between to pressing plate and pressure strip, and then produce speed discrepancy between elementary axle and secondary axle, that is to say, make friction clutch there is slippage and move.The in the situation that of there is slippage in friction clutch, the transmission of torque in the situation that of can being created in sliding friction operation at clutch disk and pressure strip and/or between to pressing plate.
In particular, elementary axle can be coupled by the first substantially consistent gear ratio and the first transmission input shaft with secondary axle, and/or elementary axle can be coupled by the second substantially consistent gear ratio and the second transmission input shaft with secondary axle.Thus, when the sealed clutch of the nonsynchronous shape of closure, remaining relatively rotates and can substantially be completely eliminated.The sealed clutch of nonsynchronous shape especially can be configured as jaw clutch, and wherein, the pawl of projection preferably has some importing rakes in the axial direction, to the pawl mutually pointing to is easily inserted.If desired, that for example by tolerance, caused, little, in the difference aspect the numerical value of gear ratio, can retain, this difference even can be so that the pawl of the mutual correspondence of jaw clutch easily inserts.In addition, jaw clutch can be in a circumferential direction to a certain extent configuration obtain and can limitedly make a concession (nachgiebig), to make easily closed nonsynchronous jaw clutch.Nonsynchronous jaw clutch for example can have sliding sleeve, and this sliding sleeve can have elastic element that elasticity can deformability in a circumferential direction with in elementary axle or secondary axle and/or corresponding transmission input shaft coupling by one.In addition likely, for the sealed clutch of the nonsynchronous shape of closure, reduce the compaction pressure of friction clutch, so as can be the shape of the sealed clutch of shape when the element of interlocking inserts mutually in locking manner in the situation that allow elementary axle to relatively rotate with respect to secondary axle for the conversion power of the sealed clutch of the nonsynchronous shape of closure is little.With respect to the first gear ratio of the first transmission input shaft with respect to the second gear ratio of the second transmission input shaft, can realize the first power transfer, wherein, rotating speed and torque can be changed and become large or conversion and diminish.This makes it possible to total gear ratio of definite speed changer shelves to be assigned to elementary axle or secondary axle with in the corresponding coupling of transmission input shaft and the coupling of corresponding transmission input shaft and transmission output shaft.Thus, total gear ratio of definite speed changer shelves can produce jointly by least two speed changer levels.This makes it possible to, for realizing definite speed changer shelves, the gear pair of saving structure space is set, thereby dual-clutch transmission is especially at the structure space needing in the radial direction still less.With respect to the first gear ratio of the first transmission input shaft, can be formed objects or Bu Tong big or small with the second gear ratio with respect to the second transmission input shaft, thereby by making elementary axle or secondary axle and the first transmission input shaft or upper with the second transmission input shaft coupling, can regulate for the sub-speed changer of correspondence the pre-gear ratio of different sizes.
Preferably, the sealed clutch of shape that is attached to the sealed clutch of shape of elementary axle and/or is attached to secondary axle can pass through a clutch element, sliding sleeve especially, with the first input shaft and with the second input shaft coupling.Thus, can form little and compactly the sealed clutch of these shapes.Especially likely, sliding sleeve both for the first transmission input shaft coupling also for the second transmission input shaft coupling, wherein, structurally can get rid of, be coupled with two transmission input shafts simultaneously.Sliding sleeve preferably can move in a neutral position, to the power stream of two transmission input shafts, on this neutral position, interrupts.Thus, needn't by means of bridge joint axle and on axially spaced locational another clutch is coupled corresponding another transmission input shaft.
Particularly preferably be, the coaxial heart layout of elementary axle and secondary axle, wherein, elementary axle is especially arranged in inner radial with respect to secondary axle.Thus, only need for elementary axle and secondary axle, little structure space.Elementary axle especially can for example be guided until the live axle of motor car engine carries out the coupling of elementary axle and live axle thereby can especially simply and save structure space ground through secondary axle.
The clutch that can skid especially has a power stage element being connected without relative rotation with secondary axle, clutch disk especially, and, be provided with one with the clutch cover of the live axle coupling of motor car engine, wherein, this clutch cover supports rotatably with respect to this secondary axle or is connected without relative rotation with this elementary axle in the situation that elementary axle is arranged in radially outer with respect to secondary axle in the situation that elementary axle is arranged in inner radial with respect to secondary axle.In the situation that secondary axle is arranged in the inner radial of elementary axle, likely, the input side of the clutch that can skid, especially friction clutch to the coupling of pressing plate and live axle, and from this input side by the torque phase that surrounds the clutch cover of power stage element at radially outer and import for secondary axle at radially outer by this clutch cover with elementary axle for example, without being connected in relative rotation, being delivered to elementary axle by the grafting tooth portion that can axially remove.This power stage element can start secondary shaft portion that pusher side goes out from elementary shaft extension, for example, by a grafting tooth portion that can axially remove, to connect without relative rotation one.In the situation that secondary axle is arranged in the radially outer of elementary axle, likely, elementary axle is direct and live axle coupling substantially, and the input side of the clutch that can skid is for example connected by a grafting tooth portion that can axially remove at the elementary shaft portion that starts pusher side to go out from secondary shaft extension without relative rotation with one.In this case, this clutch cover can be connected without relative rotation with this input side and be bearing in rotatably on the secondary axle of radially outer.Power stage element for example can be connected with secondary axle without relative rotation by a grafting tooth portion that can axially remove.
Preferably, the first transmission input shaft and the second transmission input shaft are on the ground that mutually staggers in the radial direction, preferably substantially arrange in parallel to each other.This can make elementary axle and the preferred mutually coaxial heart of secondary axle, substantially centrally be incorporated in the case of transmission of dual-clutch transmission, wherein, the first transmission input shaft and the second transmission input shaft can radially stagger and be coupled with elementary axle with secondary axle for this reason.The first transmission input shaft and the second transmission input shaft are preferably arranged in different mutually the staggering in the radial direction with respect to elementary axle and secondary axle, thereby transmission input shaft needn't mutually stagger in the axial direction and arrange, but can be arranged in a common axial region.These transmission input shafts can be in a circumferential direction preferably arranged to obtain the angle of circumference that mutually staggers on common radius at the spin axis with respect to elementary axle substantially, wherein, the transmission input shaft angle of circumference of about 180 ° that especially can mutually stagger, thus elementary axle in other words secondary axle can be arranged on common, the imaginary radial line between two transmission input shafts.This can make dual-clutch transmission radially and/or axial structure space demand keep littlely.In addition, each speed changer shelves of the first sub-speed changer and each speed changer shelves of the second sub-speed changer are ground, front and back layout in the axial direction, and wherein, likely, the speed changer shelves of corresponding sub-speed changer alternately arrange in the axial direction.In order to be coupled with the second transmission input shaft in other words with the first transmission input shaft, the gear being connected with transmission output shaft in the axial direction of different speed changer levels can be alternately set.The structure space arranging between two speed changer levels of sub-speed changer can be used by the speed changer level of another sub-speed changer of correspondence, thereby produces especially little structure space demand in the axial direction.
Particularly preferably be, one can arrange with elementary axle and/or the coaxial heart of secondary axle substantially by the transmission output shaft in the first sub-speed changer and the second sub-speed changer coupling.Thus, especially can make transmission output shaft be bearing on elementary axle and/or secondary axle by a guide bearing.In addition, avoid transmission output shaft with respect to the radial misalignments of the live axle of motor car engine, thereby for the Motor Vehicle with rear wheel drive, trailing wheel is connected on transmission output shaft simply in the motor car engine of longitudinally assembling.
The invention still further relates to a kind of method for switch dual clutch speed-changer, this dual-clutch transmission especially can form as described above and improve, wherein: first, by the sealed clutch of a nonsynchronous shape the live axle of motor car engine and and the first transmission input shaft of the first sub-speed changer coupling between produce torque flow; Subsequently, in the second sub-speed changer of not load substantially, by pre-gear selecting, the second transmission input shaft and the second sub-speed changer are coupled; Subsequently, by one can be synchronous the sealed clutch of shape make a clutch that can skid, especially power stage element and second transmission input shaft of friction clutch are coupled, and, for described torque flow is deflected into the second sub-speed changer from the first sub-speed changer, closed this clutch that can skid; Subsequently, if the torque of transmitting drops to below a predetermined threshold value, open the sealed clutch of nonsynchronous shape; Subsequently, after the rotating speed of the rotating speed of the sealed clutch of this nonsynchronous shape and the sealed clutch of shape that can be synchronous reaches adaptation, the sealed clutch of this nonsynchronous shape and the second transmission input shaft are coupled; And the clutch of subsequently, opening the sealed clutch of shape that can be synchronous and can skidding.What the method especially can as above be explained by dual-clutch transmission forms like that and improves.By means of the clutch that can skid and the sealed clutch of shape that can be synchronous, also can realize synchronizing for the sealed clutch of nonsynchronous shape, thereby for the synchronized other structural element respectively for the sealed clutch of nonsynchronous shape, especially synchronizing ring is unwanted.By save synchronizing ring can be simply and cost advantageously carry out the switching of dual-clutch transmission.By means of this method, if should be opened at the clutch skidding in service that travels normally, especially can be switched to the second sub-speed changer from the first sub-speed changer.
The invention still further relates to a kind of method for switch dual clutch speed-changer, this dual-clutch transmission especially can form as described above and improve, wherein: first, by the sealed clutch of a nonsynchronous shape the live axle of motor car engine and and the second transmission input shaft of the second sub-speed changer coupling between produce torque flow; Subsequently, in the first sub-speed changer of not load substantially, by pre-gear selecting, the first transmission input shaft and the first sub-speed changer are coupled; Subsequently, by one can be synchronous the sealed clutch of shape make a clutch that can skid, especially power stage element and first transmission input shaft of friction clutch are coupled, and, for described torque flow is deflected into the first sub-speed changer from the second sub-speed changer, closed this clutch that can skid; Subsequently, if the torque of transmitting drops to below predetermined threshold value, open the sealed clutch of nonsynchronous shape; Subsequently, after the rotating speed of the rotating speed of the sealed clutch of nonsynchronous shape and the sealed clutch of shape that can be synchronous reaches adaptation, the sealed clutch of this nonsynchronous shape and the first transmission input shaft are coupled; And the clutch of subsequently, opening the sealed clutch of shape that can be synchronous and can skidding.What the method especially can as above be explained by dual-clutch transmission forms like that and improves.By means of the clutch that can skid and the sealed clutch of shape that can be synchronous, also can realize synchronizing for the sealed clutch of nonsynchronous shape, thereby for the synchronized other structural element respectively for the sealed clutch of nonsynchronous shape, especially synchronizing ring is unwanted.By save synchronizing ring can be simply and cost advantageously carry out the switching of dual-clutch transmission.By means of this method, if should be opened at the clutch skidding in service that travels normally, especially can be switched to the first sub-speed changer from the second sub-speed changer.
The invention still further relates to a kind of method for switch dual clutch speed-changer, this dual-clutch transmission especially can form as described above and improve, wherein: first, by the sealed clutch of a nonsynchronous shape and, be arranged on clutch between the live axle of motor car engine and the sealed clutch of this nonsynchronous shape, that can skid, this live axle and and the first transmission input shaft of the first sub-speed changer coupling between produce torque flow; Subsequently, in the second sub-speed changer of not load substantially, by pre-gear selecting, the second transmission input shaft and the second sub-speed changer are coupled; Subsequently, by one can be synchronous the sealed clutch of shape live axle and the second transmission input shaft are coupled, and, for described torque flow is deflected into the second sub-speed changer from the first sub-speed changer, open the clutch that this can skid; Subsequently, if the torque of transmitting drops to below predetermined threshold value, open the sealed clutch of nonsynchronous shape; Subsequently, the clutch that closure can be skidded; Subsequently, after the rotating speed of the rotating speed of the sealed clutch of nonsynchronous shape and the sealed clutch of shape that can be synchronous reaches adaptation, the sealed clutch of this nonsynchronous shape and the second transmission input shaft are coupled; And subsequently, open can be synchronous the sealed clutch of shape.What the method especially can as above be explained by dual-clutch transmission forms like that and improves.By means of the clutch that can skid and the sealed clutch of shape that can be synchronous, also can realize synchronizing for the sealed clutch of nonsynchronous shape, thereby for the synchronized other structural element respectively for the sealed clutch of nonsynchronous shape, especially synchronizing ring is unwanted.By save synchronizing ring can be simply and cost advantageously carry out the switching of dual-clutch transmission.By means of this method, if should be closed at the clutch skidding in service that travels normally, especially can be switched to the second sub-speed changer from the first sub-speed changer.
The invention still further relates to a kind of method for switch dual clutch speed-changer, this dual-clutch transmission especially can form as described above and improve, wherein: first, by the sealed clutch of a nonsynchronous shape and, be arranged on clutch between the live axle of motor car engine and the sealed clutch of this nonsynchronous shape, that can skid, this live axle and and the second transmission input shaft of the second sub-speed changer coupling between produce torque flow; Subsequently, in the first sub-speed changer of not load substantially, by pre-gear selecting, the first transmission input shaft and the first sub-speed changer are coupled; Subsequently, by one can be synchronous the sealed clutch of shape live axle and the first transmission input shaft are coupled, and, for described torque flow is deflected into the first sub-speed changer from the second sub-speed changer, open the clutch that this can skid; Subsequently, if the torque of transmitting drops to below predetermined threshold value, open the sealed clutch of nonsynchronous shape; Subsequently, the clutch that closure can be skidded; Subsequently, after the rotating speed of the rotating speed of the sealed clutch of nonsynchronous shape and the sealed clutch of shape that can be synchronous reaches adaptation, the sealed clutch of this nonsynchronous shape and the first transmission input shaft are coupled; And subsequently, open can be synchronous the sealed clutch of shape.What the method especially can as above be explained by dual-clutch transmission forms like that and improves.By means of the clutch that can skid and the sealed clutch of shape that can be synchronous, also can realize synchronizing for the sealed clutch of nonsynchronous shape, thereby for the synchronized other structural element respectively for the sealed clutch of nonsynchronous shape, especially synchronizing ring is unwanted.By save synchronizing ring can be simply and cost advantageously carry out the switching of dual-clutch transmission.By means of this method, if should be closed at the clutch skidding in service that travels normally, especially can be switched to the first sub-speed changer from the second sub-speed changer.
The sealed clutch of shape that can be synchronous is the closure for the object of execution gear shift especially only.Thus, the only marginally load of the sealed clutch of shape that this can be synchronous, thus especially protection is the needed structural element of synchronizing rotating speed.
Accompanying drawing explanation
Below with reference to accompanying drawing, by preferred embodiment, exemplarily explain the present invention, wherein, below shown in feature both can also can represent in combination object of the present invention individually respectively.Accompanying drawing illustrates:
Fig. 1: the schematic block diagram of the dual-clutch transmission in the first mode of execution,
Fig. 2: the schematic block diagram of the dual-clutch transmission in the second mode of execution,
Fig. 3: in the time of from first grade of traction-shift-up to second gear, the time sequencing qualitative curve figure of the position of the different structure element of the dual-clutch transmission of Fig. 1 or Fig. 2,
Fig. 4: from second gear traction-retrace to the first grade time, the time sequencing qualitative curve figure of the position of the different structure element of the dual-clutch transmission of Fig. 1 or Fig. 2,
Fig. 5: in the time of from first grade of traction-shift-up to second gear, the time sequencing qualitative curve figure of the position of the different structure element of an alternative dual-clutch transmission.
Embodiment
The second transmission input shaft 14 that there is the first transmission input shaft 12 and radially stagger with this first transmission input shaft 12 abreast at the dual-clutch transmission 10 shown in Fig. 1, transmission output shaft 16 couplings that this first transmission input shaft and this second transmission input shaft can be common with.For this reason, the first transmission input shaft 12 can be connected by the second sub-speed changer 20 and output shaft 16 by the first sub-speed changer 18 and the second transmission input shaft 14.The first sub-speed changer 18 can have the first sliding sleeve 22, to be coupled the first transmission input shaft 12, for hanging into first grade or for hanging into third gear by third gear 24 by the first gear 23.Correspondingly, the second sub-speed changer 20 can have the second sliding sleeve 26, to be coupled the second transmission input shaft 14, for hanging into second gear or for hanging into fourth speed by fourth speed position 30 by the second gear 28.The first sub-speed changer 18 is connected odd number shelves, and the second sub-speed changer 20 is connected even number shelves.Especially likely, the first sub-speed changer 18 and/or the second sub-speed changer 20 can be connected other shelves by means of other gear.Each gear 23,24,28,30 of each sub-speed changer 18,20 is alternately arranged on transmission output shaft 16, thereby the gear 28,30 of the gear 23,24 of the first sub-speed changer 18 and the second sub-speed changer 20 replaces in the axial direction.Thus, can be to save the mode of structure space, as illustrated in the embodiment shown, the third gear of the first sub-speed changer 18 24 is arranged on the common axial height with respect to the second sliding sleeve 26 of the second sub-speed changer 20, and/or by fourth speed position 30(second gear 28 of the second sub-speed changer 20?) be arranged on the common axial height with respect to the first sliding sleeve 22 of the first sub-speed changer 18.
For the torque being provided by motor car engine is imported in dual-clutch transmission 10, be provided with an elementary axle 32, this elementary axle can be connected without relative rotation by member, a for example torsional vibration damper that starts the fastening flange 34 of pusher side to connect with the live axle of motor car engine or a centre, and this torsional vibration damper especially can be configured as double mass flywheel.With respect to this elementary axle 32, at radially outer, be provided with a secondary axle 36 that is configured as hollow shaft with the coaxial heart of elementary axle 32 that is configured as in the present embodiment solid shaft, this secondary axle can be configured as in clutch friction clutch 38, that can skid and 32 couplings of elementary axle by one selectively.Because friction clutch 38 can have slippage, move, likely, secondary axle 36 can have a speed discrepancy with respect to elementary axle 32.Friction clutch 38 have one be connected with elementary axle 32 without relative rotation to pressing plate 40, to can rub and compress in locking manner a clutch disk 46 being connected without relative rotation with secondary axle 36 between axially movable pressure strip 44 pressing plate 40 with respect to this by means of operation equipment 42 pressing plate and at this, for making torque flow be branched off into secondary axle 36 from elementary axle 32.Pressure strip 44 can by means of one one with the arm spring 50 supporting swingably on the clutch cover 48 that pressing plate 40 is connected, especially dish spring moves, wherein, operation equipment 42 is not fixed on clutch cap 52 substantially movingly, and arm spring 50 is supported on operation equipment 42 rotatably by bearing 54.Operation equipment 42 especially can hydraulically be operated.
In an illustrated embodiment, the coupling of elementary axle 32 and the first transmission input shaft 12 and the second transmission input shaft 14 is undertaken by the sealed clutch 64 of nonsynchronous shape, and the sealed clutch of this nonsynchronous shape is especially configured as having elementary sliding sleeve 66, without the jaw clutch of elementary synchronizing ring.Can make elementary sliding sleeve 66 move in a Zhong，Gai position, position elementary axle 32 is only coupled with the first transmission input shaft 12 by the first elementary tooth portion 56.Additionally, can make elementary sliding sleeve 66 move in a Zhong，Gai position, position elementary axle 32 is only coupled with the second transmission input shaft 14 by the second elementary tooth portion 58.In addition, can make elementary sliding sleeve 66 move to a neutral position, in this neutral position, elementary axle 32 is not neither coupled with the second transmission input shaft 14 with the first transmission input shaft 12 yet.In addition, in the embodiment shown, secondary axle 36 is undertaken by the sealed clutch 68 of the shape that can synchronize with the coupling of the first transmission input shaft 12 and the second transmission input shaft 14, the jaw clutch that the sealed clutch of shape that this can be synchronous is especially configured as having secondary sliding sleeve 70 and has secondary synchronization ring 72.Can make secondary sliding sleeve 70 move in a Zhong，Gai position, position secondary axle 36 is only coupled with the first transmission input shaft 12 by first level tooth portion 60.Additionally, can make secondary sliding sleeve 70 move to secondary axle 36 in a Zhong，Gai position, position is only coupled by second subprime tooth portion 62 and the second transmission input shaft 14.In addition, can make secondary sliding sleeve 70 move in a neutral position, in this neutral position, secondary axle 36 is not neither coupled with the second transmission input shaft 14 with the first transmission input shaft 12 yet.
Normally, travel in service, the torque flow from motor car engine to transmission output shaft on 16 especially realizes by elementary axle 32 and the sealed clutch 64 of nonsynchronous shape.For gear shift, can be in the sub-speed changer 18,20 of not load of correspondence the next desired shelves of preliminary election.Subsequently, can sealed clutch 68 couplings go up secondary axle 36 by means of shape that can be synchronous, and by closed friction clutch 38, torque flow be deflected into secondary axle 36 from elementary axle 32.After this, can open the sealed clutch 64 of nonsynchronous shape, thereby the rotating speed of the rotating speed of elementary axle 32 and secondary axle 36 can be suitable due to closed friction clutch 38.By making the rotating speed of elementary axle 32 and the rotating speed of secondary axle 36 suitable, also realize the synchronizing of elementary axle 32, thereby can be without problems the sealed clutch 64 of closed nonsynchronous shape again.After this, can open can be synchronous the sealed clutch 68 of shape and friction clutch 38, thereby after completing gear shift, produce again the operation of travelling normally, wherein, from motor car engine to transmission output shaft, the torque flow on 16 realizes by elementary axle 32 and the sealed clutch 64 of nonsynchronous shape.Alternatively, normally, travel in service, torque flow from motor car engine to transmission output shaft on 16 can in the situation that open, the sealed clutch 64 of nonsynchronous shape realizes by friction clutch 38, secondary axle 36 and the sealed clutch 68 of shape that can be synchronous, wherein, the sealed clutch 64 of closed nonsynchronous shape for gear shift only.Described above, for the flow process of gear shift without any change.Only correspondingly to change the endurance that torque flow only only realizes by secondary axle 36 in other words by elementary axle 32 therein.
Compare with the mode of execution shown in Fig. 1 of dual-clutch transmission 10, dual-clutch transmission 10 in the mode of execution shown in Fig. 2, secondary axle 36 is arranged on inner radial with respect to elementary axle 32.In this case, elementary axle 32 is configured as hollow shaft, and secondary axle 36 can be configured as solid shaft.In this case, the torque flow from motor car engine to elementary axle 32 by fastening flange 34, friction clutch 38 to pressing plate 40 with to pressing plate 40 clutch cover 48 realizations fixing, that is connected with elementary axle 32 without relative rotation.
As in Fig. 3 in time from first grade of shift-up to second gear, illustrates, normally, travel in service, can first make to be coupled with the first elementary tooth portion 56 with the elementary sliding sleeve 66 of the sealed clutch 64 of nonsynchronous shape of elementary axle 32 couplings, to can realize from motor car engine by elementary axle 32 to first transmission input shaft 12(" EW1 ") torque flow, wherein, the first transmission input shaft 12 is coupled by the first gear 23 and transmission output shaft 16 by means of the first sliding sleeve 22 of the first sub-speed changer 18.Open friction clutch 38, thus total torque being imported by motor car engine (" engine torque ") by with 32 couplings of elementary axle, the sealed clutch 64(of nonsynchronous shape " elementary-jaw clutch ") guiding.For from the first gear shift to second gear, first in the second sub-speed changer 20 that is provided for even number shelves, make the second sliding sleeve 26 and the coupling of the second gear 30, for preliminary election second gear.Thus, the second transmission input shaft 14(" EW2 ") can be essentially no load ground with rotation speed n
eW2together rotate.After this, the secondary sliding sleeve 68 by means of the sealed clutch 68 of shape that can be synchronous makes secondary axle 36 and the second transmission input shaft 14 couplings.The clutch disk 46 being connected without relative rotation with secondary axle 36 of secondary axle 36 and friction clutch 38 can in the situation that the friction clutch 38 of opening with rotation speed n S, together rotate to essentially no load thus.After this, can there is the closed friction clutch 38 in slippage ground, thereby can make the torque flow of the torque that imported by motor car engine be branched off into secondary axle 36 by friction clutch 38 from elementary axle 32.Also possible that, prior or closed friction clutch 38 of while.If total torque drops to by 36 guidings of secondary axle and the torque by elementary axle 32 guidings below the predetermined threshold of torque of transmission substantially, make the elementary sliding sleeve 66 of elementary axle 32 move in a neutral position, in this neutral position elementary axle 32 neither with the first elementary tooth portion 56 also not with 58 couplings of the second elementary tooth portion.In addition, can make the first sliding sleeve 22 of the first sub-speed changer 18 move in a neutral position, thus, the first transmission input shaft 12 unloads and can turn-off until state of rest.Under this state, the rotation speed n of the live axle of motor car engine
motwith torque can with pass through extension into second gear come given gear ratio to match.Due to friction clutch 38 closures, the rotating speed of elementary axle 32 can match with the rotating speed of secondary axle 36, thus, also finishes the slippage operation of friction clutch 38.After elementary axle 32 and secondary axle 36 synchronizings, also carry out the synchronizing of elementary axle 32 and the second transmission input shaft simultaneously, thereby after this, elementary sliding sleeve 66 can with 58 couplings of the second elementary tooth portion, to elementary axle 32 and the second transmission input shaft 14 are coupled.After this, can open friction clutch 38 and can make secondary sliding sleeve 70 move in neutral position, thereby can after gear shift, for the operation of travelling normally makes total torque stream, by elementary axle 32 and the sealed clutch 64 of nonsynchronous shape, realize again.Then, secondary axle 36 can turn-off until state of rest with the clutch disk 46 being connected without relative rotation with secondary axle 36.
As illustrated from time second gear downshift to the first grade in Fig. 4, normally, travel in service, can first make to be coupled with the second elementary tooth portion 58 with the elementary sliding sleeve 66 of the sealed clutch 64 of nonsynchronous shape of elementary axle 32 couplings, to can realize from motor car engine by elementary axle 32 to second transmission input shaft 14(" EW2 ") torque flow, wherein, the second transmission input shaft 14 is coupled by the second gear 30 and transmission output shaft 16 by means of the second sliding sleeve 26 of the second sub-speed changer 20.Open friction clutch 38, thus total torque being imported by motor car engine (" engine torque ") by with 32 couplings of elementary axle, the sealed clutch 64(of nonsynchronous shape " elementary-jaw clutch ") guiding.For from second gear gear shift to the first grade, first in the first sub-speed changer 18 that is provided for odd number shelves, make the first sliding sleeve 22 and the first gear 23 couplings, so that preliminary election second gear.Thus, can make the first transmission input shaft 12(" EW1 ") essentially no load ground is with rotation speed n
eW1together rotate.After this, the secondary sliding sleeve 68 by means of the sealed clutch 70 of shape that can be synchronous makes secondary axle 36 and the first transmission input shaft 12 couplings.The clutch disk 46 being connected without relative rotation with secondary axle 36 of secondary axle 36 and friction clutch 38 can in the situation that the friction clutch 38 of opening thus substantially non-loadedly with rotation speed n
stogether rotate.In the embodiment shown, friction clutch 38 is prior or simultaneously closed, thereby by making secondary axle 36 and the first transmission input shaft 12 couplings can there is slippage, move friction clutch 38, thereby the torque flow of the torque being imported by motor car engine can be branched off into secondary axle 36 by friction clutch 38 from elementary axle 32.If total torque drops to by 36 guidings of secondary axle and the torque by elementary axle 32 guidings below the predetermined threshold of torque of transmission substantially, make the elementary sliding sleeve 66 of elementary axle 32 move in a neutral position, in this neutral position elementary axle 32 neither with the first elementary tooth portion 56 also not with 58 couplings of the second elementary tooth portion.In this state, the rotation speed n of the live axle of motor car engine
motwith torque with pass through extension into first grade come given gear ratio to match.The rotating speed of elementary axle 32 can match due to closed friction clutch 38 and the rotating speed of secondary axle 36, thus, also finishes the slippage operation of friction clutch 38.After elementary axle 32 and secondary axle 36 synchronizings, also carry out the synchronizing of elementary axle 32 and the second transmission input shaft simultaneously, thereby after this, can make elementary sliding sleeve 66 and 56 couplings of the first elementary tooth portion, to elementary axle 32 and the second transmission input shaft 14 are coupled.After this, can open friction clutch 38 and can make secondary sliding sleeve 70 move in neutral position, thereby can after gear shift, for the operation of travelling normally makes total torque stream, by elementary axle 32 and the sealed clutch 64 of nonsynchronous shape, realize again.Then, secondary axle 36 can turn-off until state of rest with the clutch disk 46 being connected without relative rotation with secondary axle 36.In addition, can make the second sliding sleeve 26 of the second sub-speed changer 20 move in a neutral position, thus, the second transmission input shaft 14 unloads and can turn-off until state of rest.
If in servicely should realize torque flow by closed friction clutch and secondary axle 36 travelling normally, preferably the sealed clutch 64 of nonsynchronous shape is provided for to secondary axle and the sealed clutch 68 of shape that can be synchronous and is provided for elementary axle.All the other structures at the dual-clutch transmission 10 shown in Fig. 1 and Fig. 2 can retain.In this case, as take in Fig. 5 from first grade of shift-up to second gear as example is shown, normally, travel in service, first make to be coupled with first level tooth portion 60 with the secondary sliding sleeve 70 of the sealed clutch 64 of asynchronous shape of secondary axle 36 couplings, to can realize from motor car engine by closed friction clutch 38 and elementary axle 36 to first transmission input shaft 12(" EW1 ") torque flow, wherein, the first transmission input shaft 12 is coupled by the first gear 23 and transmission output shaft 16 by means of the first sliding sleeve 22 of the first sub-speed changer 18.Open the elementary sliding sleeve 66 of the sealed clutch 68 of shape that can be synchronous, thus the torque (" engine torque ") not imported by motor car engine by with the elementary axle 32 sealed clutch 68(of shape " elementary-jaw clutch " coupling, that can synchronize) guiding.For from the first gear shift to second gear, first in the second sub-speed changer 20 that is provided for even number shelves, make the second sliding sleeve 26 and the coupling of the second gear 30, so that preliminary election second gear.Thus, the second transmission input shaft 14 (" EW2 ") can be essentially no load ground with rotation speed n
eW2together rotate.After this, the elementary sliding sleeve 66 by means of the sealed clutch 68 of shape that can be synchronous makes elementary axle 32 and the second transmission input shaft 14 couplings.After this, can open friction clutch 38 and can make secondary sliding sleeve 68 move in neutral position, thereby clutch disk 46 can turn-off non-loadedly.Then, the torque being imported by motor car engine can be by elementary axle 32 guidings.In this state, the rotation speed n of the live axle of motor car engine
motwith torque can with pass through extension into second gear come given gear ratio to match.In addition, can closed friction clutch 38, thus the rotating speed of the rotating speed of secondary axle 36 and elementary axle 32 can be suitable.After this synchronizing of secondary axle 36 and elementary axle 32, also carry out the synchronizing of secondary axle 36 and the second transmission input shaft 14 simultaneously, thereby after this, secondary sliding sleeve 66 can be coupled with second subprime tooth portion 62, to make secondary axle 36 and the second transmission input shaft 14 couplings.After this, elementary sliding sleeve 66 can move in neutral position, thereby can after gear shift, for the operation of travelling normally makes total torque flow, realize again by the sealed clutch 64 of friction clutch 38, secondary axle 36 and nonsynchronous shape.Then, elementary axle 32 can turn-off until state of rest.In addition, the first sliding sleeve 22 of the first sub-speed changer 18 can move in a neutral position, and thus, the first transmission input shaft 12 unloads and can turn-off until state of rest.
The operating shift-up of inertia and/or retrace can be substantially time sequencing with in running under power, shift-up described above and/or retrace carry out similarly.
List of reference signs
10 dual-clutch transmissions
12 first transmission input shafts
14 second transmission input shafts
16 transmission output shafts
18 first sub-speed changers
20 second sub-speed changers
22 first sliding sleeves
23 first gears
24 third gears
26 second sliding sleeves
28 second gears
30 fourth speed positions
32 elementary axles
34 fastening flanges
36 level axles
38 friction clutches
40 pairs of pressing plates
42 operation equipment
44 pressure strips
46 clutch disks
48 clutch covers
50 arm springs
52 clutch caps
54 bearings
56 first elementary tooth portions
58 second elementary tooth portions
60 first level tooth portions
62 second subprime tooth portions
The sealed clutch of 64 nonsynchronous shape
66 elementary sliding sleeves
68 can be synchronous the sealed clutch of shape
70 level sliding sleeves
72 secondary synchronization rings
Claims (12)
1. for substantially not interrupting the dual-clutch transmission of the speed changer shelves of tractive force ground switching machine motor-car, have:
One first transmission input shaft (12) that can be connected with the first sub-speed changer (18), for engine torque being imported to this first sub-speed changer (18),
One second transmission input shaft (14) that can be connected with the second sub-speed changer (20), for engine torque being imported to this second sub-speed changer (20),
The one elementary axle (32) that can be connected with the live axle of motor car engine, for importing to engine torque described dual-clutch transmission (10) neutralization
One can be by a clutch that can skid, the secondary axle (36) of friction clutch (38) and described elementary axle (32) coupling especially, the engine torque being imported by this elementary axle (32) for branch,
Wherein, or
Described elementary axle (32) can pass through the sealed clutch of a nonsynchronous shape (64), especially the jaw clutch that there is no synchronizing ring, with described the first transmission input shaft (12) or with described the second transmission input shaft (14), be coupled, and, in order to make this elementary axle (32) and corresponding another transmission input shaft (14, 12) synchronizing, described secondary axle (36) can by one can be synchronous the sealed clutch of shape (68), the jaw clutch especially with synchronizing ring (72), with described the first transmission input shaft (12) or with described the second transmission input shaft (14), be coupled,
Or
Described secondary axle (36) can pass through the sealed clutch of a nonsynchronous shape (64), especially the jaw clutch that there is no synchronizing ring, with described the first transmission input shaft (12) or with described the second transmission input shaft (14), be coupled, and, in order to make this secondary axle (36) and corresponding another transmission input shaft (14, 12) synchronizing, described elementary axle (32) can by one can be synchronous the sealed clutch of shape (68), the jaw clutch especially with synchronizing ring, with described the first transmission input shaft (12) or with described the second transmission input shaft (14), be coupled.
2. according to the dual-clutch transmission of claim 1, it is characterized in that, described elementary axle (32) can be coupled by the first substantially consistent gear ratio and described the first transmission input shaft (12) with described secondary axle (36), and/or described elementary axle (32) can be by the second substantially consistent gear ratio and described the second transmission input shaft (14) coupling with described secondary axle (36).
3. according to the dual-clutch transmission of claim 1 or 2, it is characterized in that, the sealed clutch of shape (68) that is attached to the sealed clutch of shape (64) of described elementary axle (32) and/or is attached to described secondary axle (36) can pass through a clutch element, sliding sleeve (66 especially, 70), with described the first input shaft (12) with described the second input shaft (14), be coupled.
4. according to the dual-clutch transmission of any one in claims 1 to 3, it is characterized in that, the coaxial heart layout of described elementary axle (32) and described secondary axle (36), wherein, described elementary axle (32) is especially arranged in inner radial with respect to described secondary axle (36).
5. according to the dual-clutch transmission of any one in claim 1 to 4, it is characterized in that, the described clutch skidding (38) has a power stage element being connected without relative rotation with described secondary axle (36), especially clutch disk (46), and, be provided with one with the clutch cover (48) of the described live axle coupling of described motor car engine, wherein, this clutch cover (48) supports rotatably with respect to this secondary axle (36) or is connected without relative rotation with this elementary axle (32) in the situation that this elementary axle (32) is arranged in radially outer with respect to described secondary axle (36) in the situation that this elementary axle (32) is arranged in inner radial with respect to described secondary axle (36).
6. according to the dual-clutch transmission of any one in claim 1 to 5, it is characterized in that, described the first transmission input shaft (12) and described the second transmission input shaft (14) are on the ground that mutually staggers in the radial direction, preferably substantially arrange in parallel to each other.
7. according to the dual-clutch transmission of any one in claim 1 to 6, it is characterized in that, one can arrange with described elementary axle (32) and/or the coaxial heart of described secondary axle (36) substantially by the transmission output shaft (16) in described the first sub-speed changer (18) and described the second sub-speed changer (20) coupling.
8. for switching especially according to the method for the dual-clutch transmission of claim 1 to 7 any one (10), wherein,
First, by the sealed clutch of a nonsynchronous shape (64) the live axle of motor car engine and and first transmission input shaft (12) of the first sub-speed changer (18) coupling between produce torque flow,
Subsequently, in the second sub-speed changer (20) of not load substantially, by pre-gear selecting, make the second transmission input shaft (14) and described the second sub-speed changer (20) coupling,
Subsequently, by one can be synchronous the sealed clutch of shape (68) make a clutch that can skid, especially power stage element (46) and described the second transmission input shaft (14) coupling of friction clutch (38), and, for described torque flow is deflected into described the second sub-speed changer (20) from described the first sub-speed changer (18), the clutch (38) that can skid described in closed
Subsequently, if the torque of transmitting drops to below a predetermined threshold value, open the sealed clutch of described nonsynchronous shape (64),
Subsequently, after the rotating speed of the sealed clutch of described nonsynchronous shape (64) and the rotating speed of the described sealed clutch of shape (68) that can be synchronous reach adaptation, make the sealed clutch of this nonsynchronous shape (64) and described the second transmission input shaft (14) coupling and
Subsequently, open the described sealed clutch of shape (68) and the described clutch skidding (38) that can be synchronous.
9. for switching especially according to the method for the dual-clutch transmission of claim 1 to 7 any one (10), wherein,
First, by the sealed clutch of a nonsynchronous shape (64) the live axle of motor car engine and and second transmission input shaft (14) of the second sub-speed changer (20) coupling between produce torque flow,
Subsequently, in the first sub-speed changer (18) of not load substantially, by pre-gear selecting, make the first transmission input shaft (12) and described the first sub-speed changer (18) coupling,
Subsequently, by one can be synchronous the sealed clutch of shape (68) make a clutch that can skid, especially power stage element (46) and described the first transmission input shaft (12) coupling of friction clutch (38), and, for described torque flow is deflected into described the first sub-speed changer (18) from described the second sub-speed changer (20), the clutch (38) that can skid described in closed
Subsequently, if the torque of transmitting drops to below predetermined threshold value, open the sealed clutch of described nonsynchronous shape (64),
Subsequently, after the rotating speed of the sealed clutch of described nonsynchronous shape (64) and the rotating speed of the described sealed clutch of shape (68) that can be synchronous reach adaptation, make the sealed clutch of this nonsynchronous shape (64) and described the first transmission input shaft (12) coupling and
Subsequently, open the described sealed clutch of shape (68) and the described clutch skidding (38) that can be synchronous.
10. for switching especially according to the method for the dual-clutch transmission (10) described in claim 1 to 7 any one, wherein,
First, by the sealed clutch of a nonsynchronous shape (64) and, be arranged on clutch (38) between the live axle of motor car engine and the sealed clutch of this nonsynchronous shape (64), that can skid, described live axle and and first transmission input shaft (12) of the first sub-speed changer (18) coupling between produce torque flow
Subsequently, in the second sub-speed changer (20) of not load substantially, by pre-gear selecting, make the second transmission input shaft (14) and described the second sub-speed changer (20) coupling,
Subsequently, by one can be synchronous the sealed clutch of shape (68) make the coupling of described live axle and described the second transmission input shaft (14), and, for described torque flow is deflected into described the second sub-speed changer (20) from described the first sub-speed changer (18), open the described clutch (38) that can skid
Subsequently, if the torque of transmitting drops to below predetermined threshold value, open the sealed clutch of described nonsynchronous shape (64),
Subsequently, the clutch (38) that can skid described in closed,
Subsequently, after the rotating speed of the sealed clutch of described nonsynchronous shape (64) and the rotating speed of the described sealed clutch of shape (68) that can be synchronous reach adaptation, make the sealed clutch of this nonsynchronous shape (64) and described the second transmission input shaft (14) coupling and
Subsequently, open the described sealed clutch of shape (68) that can be synchronous.
11. for switching especially according to the method for the dual-clutch transmission of claim 1 to 7 any one (10), wherein,
First, by the sealed clutch of a nonsynchronous shape (64) and, be arranged on clutch (38) between the live axle of motor car engine and the sealed clutch of this nonsynchronous shape (64), that can skid, described live axle and and second transmission input shaft (14) of the second sub-speed changer (20) coupling between produce torque flow
Subsequently, in the first sub-speed changer (18) of not load substantially, by pre-gear selecting, make the first transmission input shaft (12) and described the first sub-speed changer (18) coupling,
Subsequently, by one can be synchronous the sealed clutch of shape (68) make the coupling of described live axle and described the first transmission input shaft (12), and, for described torque flow is deflected into described the first sub-speed changer (18) from described the second sub-speed changer (20), open the described clutch (38) that can skid
Subsequently, if the torque of transmitting drops to below predetermined threshold value, open the sealed clutch of described nonsynchronous shape (64),
Subsequently, the clutch (38) that can skid described in closed,
Subsequently, after the rotating speed of the sealed clutch of described nonsynchronous shape (64) and the rotating speed of the described sealed clutch of shape (68) that can be synchronous reach adaptation, make the sealed clutch of this nonsynchronous shape (64) and described the first transmission input shaft (12) coupling and
Subsequently, open the described sealed clutch of shape (68) that can be synchronous.
The method of any one in 12. according to Claim 8 to 11, wherein, by the described sealed clutch of shape (68) closure for carrying out the object of gear shift only that can be synchronous.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012209999.9 | 2012-06-14 | ||
| DE102012209999.9A DE102012209999B4 (en) | 2012-06-14 | 2012-06-14 | Dual clutch transmission and method for shifting a dual clutch transmission |
Publications (2)
| Publication Number | Publication Date |
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| CN103511614A true CN103511614A (en) | 2014-01-15 |
| CN103511614B CN103511614B (en) | 2017-06-13 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201310232728.2A Expired - Fee Related CN103511614B (en) | 2012-06-14 | 2013-06-13 | Dual clutch transmission and method for shifting a dual clutch transmission |
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| Country | Link |
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| CN (1) | CN103511614B (en) |
| DE (1) | DE102012209999B4 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105673729A (en) * | 2014-12-05 | 2016-06-15 | 奥特润株式会社 | Slip factor learning method of dual clutch transmission |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2565749C1 (en) * | 2014-04-08 | 2015-10-20 | Юрий Леонидович Евтодеев | Compact seven-stage transmission with two clutches |
| RU2565799C1 (en) * | 2014-04-08 | 2015-10-20 | Юрий Леонидович Евтодеев | Heptacyclic gearbox with dual clutch |
| DE102015216593B4 (en) | 2015-08-31 | 2020-07-09 | Schaeffler Technologies AG & Co. KG | Powershift transmission and powertrain with this |
| DE102016220217A1 (en) | 2016-10-17 | 2018-04-19 | Schaeffler Technologies AG & Co. KG | Method for controlling a drive train with a dual-clutch transmission |
| CN106704408B (en) * | 2016-12-28 | 2023-07-21 | 四川省机械研究设计院(集团)有限公司 | Controllable mechanical soft start system and method |
| CA3052386A1 (en) * | 2019-08-16 | 2021-02-16 | Joel SULLIVAN | Transmission with averaging differential |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102004020955A1 (en) * | 2004-04-28 | 2005-12-15 | Zf Friedrichshafen Ag | Manual transmission in countershaft design |
| US20080196543A1 (en) * | 2007-02-16 | 2008-08-21 | Aisin Ai Co., Ltd. | Gear-type transmission apparatus |
| GB2424250B (en) * | 2005-03-17 | 2010-06-02 | Ford Global Tech Llc | Dual clutch kinematic arrangements with wide span |
| CN101044344B (en) * | 2004-08-27 | 2010-06-16 | Gm全球科技运作股份有限公司 | Powershift gearbox and shifting method therefor |
| CN102252042A (en) * | 2010-05-19 | 2011-11-23 | 通用汽车环球科技运作有限责任公司 | Shift transmission synchronizer |
-
2012
- 2012-06-14 DE DE102012209999.9A patent/DE102012209999B4/en not_active Expired - Fee Related
-
2013
- 2013-06-13 CN CN201310232728.2A patent/CN103511614B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102004020955A1 (en) * | 2004-04-28 | 2005-12-15 | Zf Friedrichshafen Ag | Manual transmission in countershaft design |
| CN101044344B (en) * | 2004-08-27 | 2010-06-16 | Gm全球科技运作股份有限公司 | Powershift gearbox and shifting method therefor |
| GB2424250B (en) * | 2005-03-17 | 2010-06-02 | Ford Global Tech Llc | Dual clutch kinematic arrangements with wide span |
| US20080196543A1 (en) * | 2007-02-16 | 2008-08-21 | Aisin Ai Co., Ltd. | Gear-type transmission apparatus |
| CN102252042A (en) * | 2010-05-19 | 2011-11-23 | 通用汽车环球科技运作有限责任公司 | Shift transmission synchronizer |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105673729A (en) * | 2014-12-05 | 2016-06-15 | 奥特润株式会社 | Slip factor learning method of dual clutch transmission |
| CN105673729B (en) * | 2014-12-05 | 2018-12-28 | 奥特润株式会社 | The slide coefficient learning method of double-clutch speed changer |
| US10252723B2 (en) | 2014-12-05 | 2019-04-09 | Hyundai Autron Co., Ltd. | Slip factor learning method of dual clutch transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102012209999A1 (en) | 2013-12-19 |
| CN103511614B (en) | 2017-06-13 |
| DE102012209999B4 (en) | 2016-03-17 |
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