WO2001061212A1 - Drehmomentübertragungsvorrichtung, insbesondere mit doppelkupplungsgetriebe - Google Patents
Drehmomentübertragungsvorrichtung, insbesondere mit doppelkupplungsgetriebe Download PDFInfo
- Publication number
- WO2001061212A1 WO2001061212A1 PCT/DE2001/000217 DE0100217W WO0161212A1 WO 2001061212 A1 WO2001061212 A1 WO 2001061212A1 DE 0100217 W DE0100217 W DE 0100217W WO 0161212 A1 WO0161212 A1 WO 0161212A1
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- Prior art keywords
- shaft
- transmission device
- torque transmission
- torque
- clutch
- Prior art date
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Classifications
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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
- 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
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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
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
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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
- F16H61/68—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 specially adapted for stepped gearings
- F16H61/684—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 specially adapted for stepped gearings without interruption of drive
- F16H61/688—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 specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by clutches
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19019—Plural power paths from prime mover
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19223—Disconnectable counter shaft
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19233—Plurality of counter shafts
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19251—Control mechanism
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19284—Meshing assisters
- Y10T74/19288—Double clutch and interposed transmission
Definitions
- Torque transmission device in particular with double clutch transmission
- the invention relates to a torque transmission device, which in particular has a double clutch transmission.
- a torque transmission device is already known, which is designed as a double clutch transmission (cf. G. Lechner, H. Naunheimer; vehicle transmission; Berlin 1994).
- This double clutch transmission has a transmission input shaft which is divided into a solid and a hollow shaft. Two lines are available for the power flow. One clutch operates the second and fourth gears and a second clutch the first and third gears. The gears of the inactive line can be preselected. The gear change then takes place by changing over from one clutch to the other.
- the invention has for its object to provide a differently designed torque transmission device.
- the invention has for its object to provide a differently designed torque transmission device which has a dual clutch transmission.
- the invention has for its object to provide a torque transmission device which is structurally simple and inexpensive to manufacture and which, particularly in a motor vehicle, ensures good comfort.
- control device for controlling a torque transmission device which has at least one feature of the features which are described in the following description or in the claims or are shown in the figures.
- the object is further achieved by a method for operating a torque transmission device which has at least one feature of the features which are described in the following description or the claims or are shown in the figures.
- the object is further achieved by a torque transmission device according to claim 1 or claim 2 or claim 4 or claim 6.
- the object is further achieved by a control device for controlling a torque transmission device according to claim 54.
- the object is further achieved by a method for operating a torque transmission device according to claim 55.
- a torque transmission device has at least one first, at least one second and at least one third shaft, and a transmission device.
- the first and / or second and / or third shaft is at least partially a component of the transmission device or is arranged outside the transmission device.
- a torque transmission device is a device which can transmit a torque and which can be switched to different switching positions.
- a torque transmission device in the sense of the present invention preferably has at least one clutch device and at least one transmission device.
- a transmission device is, in particular, a device which can be shifted in steps or steplessly and with or without interruption of tractive power in a different shift position by generating a different transmission ratio between two predetermined shafts.
- the control of switching operations of the transmission device can automatically be designed table or by hand or semi-automatically or automatically with additional intervention options by hand or in another way. Switching operations of the transmission device are controlled electronically in particular.
- the gear mechanism is particularly preferably designed in such a way that it is possible to switch between different gear ratios without interrupting the tractive force.
- a transmission stage in the sense of the present invention is in particular components of a transmission device, such as gear wheels, which can cause a torque to be transmitted between two predetermined shafts.
- the transmission device has a plurality of different transmission stages, of which a part can be switched between the first shaft and the third shaft and of which a part can be switched between the second shaft and the third shaft.
- a torque is transmitted directly or indirectly between the first and the third shaft or the second and the third shaft.
- the torque between the first shaft and the third shaft or the second shaft and the third shaft is transmitted indirectly.
- direct transmission is to be understood to mean that a torque from a shaft or a component which is coupled in a rotationally fixed manner to this shaft is introduced directly into the other shaft or a component which is coupled in a rotationally fixed manner to this shaft without the interposition of further components.
- indirect transmission of the torque is understood to mean that the torque is introduced from one shaft or a component connected to this shaft in a rotationally fixed manner into an intermediate component or an arrangement of intermediate components, and from this intermediate component the torque to the other shaft or a component connected to it in a rotationally fixed manner is passed on.
- the torque transmission can take place via gear wheels or belt means or in some other way.
- the toothing of the gears is straight toothed or very toothed or designed in some other way.
- the gearwheels can in particular be bevel gears or spur gears and internal or external gears.
- the torques can in particular also be transmitted via friction wheels.
- at least one transmission stage which can be switched between the first shaft and the third shaft, has the same transmission ratio as a transmission stage, which can be switched between the second shaft and the third shaft.
- gear ratios can be switched between the first shaft and the third shaft and some of the gear ratios can be switched between the second shaft and the third shaft.
- the transmission device is designed such that the torque flow through the torque transmission device via a transmission stage arranged between the first and the third shaft or alternatively via a transmission stage arranged between the second and the third shaft or both via an arrangement arranged between the first shaft and the third shaft Translation stage as well as a translation stage arranged between the second wave and the third wave can flow.
- the object is further achieved by a torque transmission device according to claim 2.
- a torque transmission device has at least one first, at least one second and at least one third shaft, and a transmission device.
- the transmission device can be switched to different switching positions.
- the transmission device also has a plurality of gear ratios, which differ at least partially by the gear ratios that are or can be switched in these gear ratios. Some of these gear ratios can be between the first and third waves can be switched and part of these gear ratios can be switched between the second shaft and the third shaft.
- a torque transmission device is integrated in a motor vehicle, which has a motor vehicle drive device which is preferably designed as an internal combustion engine and loads a crankshaft in a predetermined direction of rotation.
- a motor vehicle drive device which is preferably designed as an internal combustion engine and loads a crankshaft in a predetermined direction of rotation.
- gear ratios are preferably designed in such a way that with this direction of rotation of the crankshaft in the different gear ratios the same direction of rotation of the third shaft is effected, the gear ratios preferably being arranged in the torque flow between the crankshaft and the third shaft or in this torque foot can be switched.
- gear ratios are preferably designed in such a way that when the crankshaft has a direction of rotation predetermined by the motor vehicle drive device, a direction of rotation of the third shaft is generated, which causes the motor vehicle to be driven in the forward direction.
- At least one further transmission stage is designed in such a way that, under the predetermined conditions, an opposite direction of rotation of the third shaft is brought about.
- the torque transmission device according to the invention is particularly preferably arranged in a motor vehicle with a motor vehicle drive device, crankshaft, and at least one vehicle drive axis, the direction of rotation of the crankshaft, which is determined by the motor vehicle drive device, causing this opposite direction of rotation of the third shaft, which in turn causes that the vehicle is driven in the reverse direction.
- This reversal of the direction of rotation is particularly preferably effected in that a translation stage between the first and the third or the second and the third shaft is divided at least once into partial translations.
- the first direction of rotation of the third shaft or the forward gears are particularly preferably generated in such a way that the shift stages are designed as an arrangement of gearwheels, with a gearwheel connected in a rotationally fixed manner to the first or second shaft engaging directly in a gearwheel connected to the third shaft to effect the first direction of rotation of the third shaft.
- an intermediate gear stage is additionally arranged between a gearwheel arranged on the first or second shaft and a gearwheel arranged on the third shaft.
- the ratios which are arranged between the first and the third or the second and the third shaft and cause a first direction of rotation of the third shaft or a direction of rotation of a drive axle of a motor vehicle, which is designed such that the vehicle is driven in the forward direction , are numbered with increasing translation of the respective gear ratio or with increasing overall gear ratio of the total gear ratios assigned to these respective gear levels, namely with consecutive natural numbers and starting with the number 1.
- the translation of the translation stage is to be understood in particular to mean the translation which is assigned to a gear or transmission stage, which may be subdivided into sub-stages, and which is arranged between the first shaft and the third shaft or the second shaft and the third shaft ,
- the overall gear ratio of the gear train assigned to this gear ratio is to be understood in particular as the gear ratio between the crankshaft of a motor vehicle and a predetermined drive axle of this motor vehicle, which is given when the predetermined gear ratio between the first shaft and the third shaft or the second shaft and the third Shaft is switched.
- the natural numbers assigned to these gear ratios correspond in particular to the gears of a motor vehicle.
- at least one translation stage can be switched, which is denoted by an even number, and at least one translation stage which is denoted by an odd number.
- a torque is transmitted from the transmission device when shifting between different switching or transmission stages of the transmission device, so that a gear change under load is made possible.
- the object is further achieved by a torque transmission device according to claim 4.
- the torque transmission device has a plurality of shafts, of which at least one is a third and at least one is a fourth shaft.
- the fourth shaft is preferably an input shaft, such as, for example, an input shaft of the torque transmission device or a transmission input shaft
- the third shaft is an output shaft, such as, for example, a transmission output shaft or an output shaft of the torque transmission device or a drive axle of a motor vehicle.
- a transmission device is at least partially arranged in the transmission path between the third and fourth shafts under predetermined conditions and can be shifted into different switching positions. At least some of these switch positions differ in that the gear ratio between the third and fourth waves is different. Torque can be transmitted between the third shaft and the fourth shaft during a switching operation between different switching positions or different gear ratios. In at least two different switching positions, the switched ratio between the third and fourth waves is identical. It is also preferred that several groups of the shift positions each have an identical, but different between the groups, gear ratio of the transmission device.
- At least one of the waves is preferably a first wave and at least one of the waves is a second wave and at least one of the waves is a third wave
- the Gear device can be switched to different switching positions and in these different switching positions there are at least partially different gear ratios and some of these gear ratios can be switched between the first and third shafts and some of these gear ratios between the second and third shafts.
- the object is further achieved by a torque transmission device according to claim 6.
- a torque transmission device is provided with at least one first, at least one second and at least one third shaft, which furthermore has a transmission device.
- the transmission device can be switched to different switching positions and has several different gear ratios. Some of these gear ratios can be switched between a first shaft and the third shaft and some of these gear ratios can be switched between the second shaft and the third wave.
- the translation levels are numbered in the direction of increasing translation or overall translation with consecutive natural numbers.
- the transmission device is also designed in such a way that from at least one predetermined gear ratio between the first and third or the second and third shafts, which in particular is associated with a predetermined gear of the motor vehicle, it is possible to shift to the gear ratios which have the two next higher numbers are provided and / or can be switched to the gear ratios which are denoted by the next two lower numbers, the torque transmission device transmitting torque during these switching operations, that is to say in particular torque from a crankshaft of a motor vehicle with a torque transmission device to the drive axles of this motor vehicle is transmitted while switching between these different gears. It is also particularly preferred that it is possible to shift from one gear to the next three higher and / or lower gears or to shift to the next four higher and / or next four lower gears.
- a plurality of first and a plurality of second shafts are particularly preferably provided according to the invention, intermediate shafts possibly being connected between these first or second shafts and the third shaft.
- Shifting into the two or three or four next higher or next lower gear stages is to be understood in particular to mean that any of these gear stages can be selected into which the gear is shifted, and that without interruption of tractive power in the drive train.
- the torque transmission device or transmission device preferably has six forward gears and one reverse gear, the first, third, fourth and sixth forward gears being assigned gear ratios which are arranged between the first and third shafts, and the reverse gear, the second gear, the fourth gear and the fifth gear are assigned transmission stages which are arranged between the second shaft and the third shaft.
- the fourth gear is preferably arranged both between the first and the third shaft and between the second and the third shaft.
- first and further second shafts are provided and gear ratios assigned to a plurality of respectively predetermined gears can be shifted several times, that is to say in different shift positions of the transmission device, shift processes can be shifted into any next higher realize here or any next lower gear stages, the traction in the drive train is not interrupted during these switching operations.
- a plurality of translations or overall translations which are assigned to the translation stages between the first shaft and the third shaft, can also be switched in transmission stages between the second shaft and the third shaft.
- Each shiftable gear can particularly preferably be engaged both by shifting a corresponding transmission stage between the first and the third shaft and by shifting a corresponding transmission stage between the second shaft and the third shaft, so that in this preferred Embodiment can be switched from any gear to any other gear.
- the transmission device or the torque transmission device is electronically controlled.
- the torque transmission device preferably has at least one clutch device, preferably at least one first and at least one second clutch device. Particularly preferably, the torque transmission device has, if necessary additionally, at least one third clutch device.
- the coupling devices are designed with or without a power split and can transmit torque by friction, form locking or in some other way.
- the first and the second clutch device are preferably friction clutches which have two or more friction surfaces.
- the first and second clutch devices are a multi-plate clutch or other friction clutch and the third clutch devices are dog clutches.
- the coupling devices can be designed with or without a synchronization device.
- the synchronization device enables in particular that the speed of these parts can be adjusted when engaging two rotatably mounted parts before engaging.
- the coupling devices can be designed to run wet or as a dry coupling.
- the first and the are particularly preferred second clutch device designed as a wet-running multi-plate clutch or as a dry friction clutch.
- the coupling devices are designed to be self-adjusting or not to be self-adjusting and optionally have a spring or damper or spring-damper device.
- This spring or damper or spring damper device is preferably coupled to the friction linings of a friction clutch.
- At least one wheel is preferably arranged around the axis of the first and / or the second and / or the third and / or the fourth shaft or the input shaft and / or the output shaft.
- This wheel can particularly preferably be used for torque transmission, if appropriate in combination with wheels which are arranged on others above the shafts.
- At least a part of these wheels is preferably designed as an externally or internally toothed spur gear or as a bevel gear or as a hypoid gear or as a helical gear or as a worm gear or as a friction wheel.
- the concept of the friction wheel is to be understood broadly within the meaning of the present invention and includes, in particular, friction wheels which are designed in such a way that they transmit torque through direct engagement in one or more further friction wheels, or that they are applied by means of a belt Torque transmitted.
- a torque is transmitted between toothed wheels by means of a belt.
- a preferred transmission device has a plurality of third coupling devices.
- These third coupling devices are particularly preferably arranged, at least in part, in such a way that they are each assigned to at least one translation stage which is arranged between the first and third shafts or the second and third shafts and that they can effect that a torque can be transmitted from the first shaft via the respective transmission stage to the third shaft or vice versa, or that the torque transmission is not possible.
- the third coupling devices are particularly preferably arranged in the region of the second and the third shaft.
- the third clutch devices are preferably designed as a dog clutch and particularly preferably have a synchronization device. This synchronization device has in particular synchronization rings.
- a rotationally fixed connection can preferably be produced or released between a gearwheel arranged on the first shaft and the first shaft, or a rotationally fixed connection of this gearwheel with the second shaft can be produced or released between a gearwheel arranged on the second shaft, wherein the coupling device is switched in different switching positions.
- the gears arranged on the first and second shafts of these, in particular the gears assigned, gear ratios are rotatably mounted on the respective shafts and can be connected in a rotationally fixed manner to the respective shaft via the respective third coupling device.
- At least one of the third clutch devices can connect a plurality of wheels mounted on the first or the second shaft in a rotationally fixed manner to this respective shaft or release this connection.
- this respective coupling device is preferably designed such that at the same time only one of the wheels which can be coupled to the respective shaft is connected to this shaft in a rotationally fixed manner.
- the transmission device of the torque transmission device can preferably be shifted into n gear ratios or gears, with (nm) third clutch devices being provided and with n and m being natural numbers.
- n (n + 1) / 2 if n is an odd number
- m (n + 2) / 2 if n is an even number.
- the transmission device can be shifted into eight gear ratios or gears, n third clutch devices being provided.
- the transmission device can preferably be shifted into seven gear ratios or gears, four third clutch devices also being provided.
- the eight gears are in particular six different forward gears, one reverse gear, and another forward gear that is identical to one of the six forward gears.
- bankss- Two fourth forward gears are provided.
- the seven gears are in particular five forward gears, one reverse gear, and one gear that is identical to one of the five forward gears.
- the invention is not intended to be limited to these special gears.
- a plurality of reverse gears or fewer than five or more than six forward gears can also be provided. It is further preferred that not only one gear stage or one gear can be engaged multiple times, that is to say different shift positions of the transmission device are provided, in which the same gear is engaged, but several gears are given twice.
- the first and / or the second and / or the third clutch devices are each actuated or switched by an actuating device.
- the actuating devices of the third clutch device can be designed in such a way that one actuating device is provided for each one gear ratio or one gear or that several gears or gear ratios can be actuated by one actuating device.
- the actuating devices preferably have a drive device or are coupled to a drive device.
- the drive devices and the actuating devices can each be designed hydraulically and / or pneumatically and / or electrically and / or electromechanically or only mechanically or in some other way.
- first actuation devices or drive devices the actuation devices which actuate first clutch devices and the associated drive devices are referred to in particular as first actuation devices or drive devices, while the actuation device or the associated drive device of the second clutch device in particular as second drive or actuation device and during which while the actuating devices or the associated drive devices of the third clutch devices are referred to in particular as third drive or actuating devices.
- the transmission path between these respective drive devices and these respective coupling devices can be with at least one or without Translation stage be trained. It is further preferred that a translation stage is provided within at least one of these drive devices.
- the torque transmission device has at least two third clutch devices, each of which can be loaded by a third, possibly common, drive device, the respective signal transmission paths between this or these third drive devices and the associated third clutch devices for these third clutch devices is partially identical.
- This is realized in particular in that at least some of the same components are used to transmit the signal transmitted from the respective third drive device to the respective third clutch device and / or in that these components are loaded in the same way when these different third clutch devices are loaded.
- a switching shaft is preferably arranged in the signal transmission path between two different third clutch devices and the associated third drive devices, which shift shaft can be loaded rotationally by one of the third drive devices and translationally by another of the third drive devices. It is particularly preferred that by switching the shift shaft in the translational direction it can be determined which of the third clutch devices is to be engaged or disengaged and the corresponding engagement and disengagement can be carried out by rotating this shift shaft.
- Such an arrangement which has the switching and selecting function, is particularly preferably provided for the third clutch devices of the first shaft and such an arrangement for the third clutch devices of the second shaft.
- a plurality of third coupling devices are provided which have a signal transmission path to their respective drive device which is provided exclusively for this third coupling device, so that this signal transmission path or its components are not used by a plurality of third coupling devices or for switching these third coupling devices become.
- the third clutch device which is assigned to the first shaft, can preferably be switched independently of the third clutch device, which is assigned to the second shaft.
- the coupling devices assigned to these first shafts can be particularly preferably switched independently of the coupling devices of other first shafts or other second shafts.
- a third drive device is particularly preferably provided for each third clutch device. At least one of the third actuating devices preferably has a shift drum.
- a shift drum is to be understood in particular as a component which can be loaded by a drive device and which has a profiling by means of which a positive control is implemented.
- the shift drum is particularly preferably loaded rotationally or translationally by a drive device, such as an electric motor, the shift drum being designed essentially as a cylindrical body with profiled recesses arranged on the outer circumference, into which a plurality of shift forks or the like engage.
- the shift forks also engage in the clutch device, in particular the third clutch devices.
- the individual third clutch devices can be actuated, in particular in such a way that it is ensured that not several gear stages with different ratios are shifted at the same time.
- a shift drum is particularly preferably provided for the or for each first shaft and for the or for each second shaft or the third clutch devices assigned to these shafts.
- the torque transmission device of the invention operates at least one about the axis of the first shaft disposed wheel and at least one disposed about the axis of the second shaft wheel on a same wheel which is arranged around the axis of the third shaft, wherein in particular the order the first and the second shaft arranged wheel can be rotatably coupled with this respective shaft or can be uncoupled from this shaft.
- Each of these wheels is used to design a gear ratio between the first and third shafts or between the second and third shafts.
- the gear ratios between the first shaft and the third shaft or the second shaft and the third shaft, which can be switched using this wheel of the third shaft, which wheel is used by both the first and the second shaft for torque transmission, can be identical or different .
- torque can be transmitted from a plurality of wheels extending around the axis of the third shaft, both from the first and from the second shaft.
- a wheel arranged on the third shaft can be used on the one hand to shift a first gear and on the other hand to shift the reverse gear.
- a predetermined gear such as fourth gear
- a predetermined gear can be engaged by means of a wheel of the third shaft and a wheel of the first shaft or by means of this wheel of the third shaft and a wheel of the second shaft. If this gear is shifted, it is particularly preferred to transmit the torque both between the second and the third shaft and between the first and the third shaft, the first and the second clutch device being at least temporarily completely closed.
- At least one wheel of the third shaft by means of a wheel of the first shaft during a first time window and by means of a wheel torque is transmitted to the second shaft during a second time window different from the first.
- the coupling device according to the invention is preferably designed in such a way that, under predetermined conditions, a torque can be transmitted from the first shaft as well as from the second shaft to the third shaft, a torque by means of a wheel of the third shaft being transmitted from the first shaft to the third shaft is initiated and wherein a torque is introduced from the second shaft into the third shaft by means of another wheel, different from the aforementioned wheel, of the third shaft.
- These torques of the first and the second shaft can be generated by the same drive device, and in particular transmitted to the first shaft and the second shaft via the crankshaft of a motor vehicle with a torque transmission device according to the invention, with the torque flowing between the crankshaft and the first shaft and a clutch device is arranged in the torque flow between the crankshaft and the second shaft, and particularly preferably the torque is transmitted to the first shaft by means of a first clutch device and the torque to the second shaft by means of a second clutch device.
- the first clutch device and the second clutch device have a common clutch housing.
- the first clutch device is designed such that it transmits torque between a fifth shaft and a sixth shaft in at least one first switching position and is open in at least one second switching position so that it does not transmit any torque between these shafts can.
- this first clutch device can also be switched to at least a third switching position, in which it can transmit a predetermined, limited torque between the fifth and the sixth shaft.
- the first clutch device is designed as a friction clutch, so that it slips if the applied torque to be transmitted becomes greater than the predetermined torque.
- the fifth shaft is in particular a crankshaft of a motor vehicle
- the sixth shaft is in particular a first or a second or a fourth shaft or an input shaft, such as a transmission input shaft.
- the second coupling means is rotatably mounted in particular on the sixth shaft.
- This is achieved in particular by the fact that the output part of the first coupling device facing the output is connected in a substantially rotationally fixed manner to the sixth shaft, around which the output part of the second coupling device rotates, and possibly concentrically.
- This output part of the second coupling device is preferably coupled to a wheel in a substantially rotationally fixed manner.
- the sixth period is particularly preferably coupled in a rotationally fixed manner to a wheel.
- a torque is preferably transmitted to the first shaft or the second shaft via these respective wheels.
- the second coupling device preferably transmits a torque between a seventh shaft and an eighth shaft in at least a first switching position of this second coupling device and interrupts this torque flow through the second coupling device in at least a second switching position.
- the second clutch device can also be switched to at least a third switching position, in which it can transmit a predetermined, limited torque.
- the second clutch device is particularly preferably designed as a friction clutch device, wherein it slips when this predetermined torque is exceeded.
- the seventh shaft is in particular the fifth shaft or the crankshaft of a motor vehicle or a component that is coupled to this crankshaft in a rotationally fixed manner.
- the eighth wave is in particular one of the first or one of the second or the fourth wave.
- the first and / or the second clutch device is preferably arranged in the torque flow between the crankshaft of a motor vehicle with the transmission device and the first and the second shaft.
- the first and / or the second clutch device is preferably arranged in the torque flow between the first and the second shaft and a drive axle of a motor vehicle.
- the first and the second clutch device simultaneously transmit a torque under predetermined conditions, which torque is transmitted in particular to the first shaft or the second shaft.
- the limit torque that can be transmitted by the first clutch device or by the second clutch device is particularly preferably limited to a predetermined value.
- the torque transmission device preferably has a control device which controls the shift positions of the first and the second clutch device according to a predetermined characteristic.
- This control device particularly preferably also controls the third clutch devices and possibly further switching operations or the like.
- the first clutch device and the second clutch device are switched at least temporarily simultaneously under predetermined circumstances, in particular one of these clutch devices increasingly being opened and the other of these clutch devices being increasingly closed.
- the first and the second clutch device are switched in the manner of an overlap circuit.
- one of these two coupling devices is completely closed, while the other of these two coupling devices is opened completely.
- One clutch device is increasingly opened, while the other is increasingly closed, so that torque is increasingly transmitted via the other clutch device and the torque transmission via the one clutch is reduced.
- the other clutch device is completely closed and the one clutch device is completely open.
- the torque transmission device can transmit a torque from the crankshaft of a motor vehicle with a torque transmission device to a drive axle of this motor vehicle during the entire switching process between the gears, or vice versa.
- the third shaft is in particular an input shaft, such as an input shaft of the torque transmission device or the transmission device, or an output shaft, such as an output shaft of the torque transmission device or the transmission device.
- the fourth shaft is in particular an input shaft, such as an input shaft of the torque transmission device or the transmission device, or an output shaft, such as an output shaft of the torque transmission device or the transmission device.
- the torque transmission device has at least a fourth clutch device.
- the first and / or the second and / or the fourth clutch device are preferably designed as a starting clutch.
- the torque transmission device particularly preferably has a first, a second, a plurality of third and a fourth clutch device.
- the fourth clutch device is particularly preferably designed as a starting clutch, an input part of this fourth clutch device being coupled in a rotationally fixed manner to the crankshaft of a motor vehicle.
- the third clutch devices are assigned to the transmission stage of the transmission device and are preferably designed in such a way as has already been described above.
- the first and the second clutch device which are each preferably designed as a multi-disk clutch, can couple and decouple the first shaft and a fourth shaft or output shaft or the second shaft and a fourth shaft or output shaft.
- the transmission stages of the transmission device are preferably arranged between a third shaft and the first shaft or between the third shaft and the second shaft.
- the third shaft is in particular a transmission input shaft.
- the object is further achieved by a control device for controlling a torque transmission device according to claim 54.
- the object is further achieved by a method according to claim 55.
- taxes in the sense of the present invention is to be understood in particular as “rules” and / or “taxes” in the sense of DIN. The same applies to terms derived from the term “taxes”.
- FIG. 1 shows a first schematic, partially sectioned view of a torque transmission device according to the invention
- FIG. 2 shows a simplified view according to FIG. 1;
- FIG. 3 shows a view in which exemplary switching operations are symbolized on the basis of the representation according to FIG. 2;
- FIG. 4 shows a second view in which exemplary switching operations are symbolized on the basis of the representation according to FIG. 2;
- Fig. 5 is a third view in which exemplary switching operations based on the
- FIG. 6 shows a table of possible switching operations that can be switched under load in an exemplary embodiment according to FIG. 1;
- FIG. 7 shows a second exemplary embodiment of the invention in a schematic, partially sectioned view
- FIG. 8 shows a third exemplary embodiment of the invention in a schematic, partially sectioned view
- FIG. 9 shows a fourth exemplary embodiment of the invention in a schematic, partially sectioned view
- FIG. 10 shows a fifth exemplary embodiment of the invention in a schematic, partially sectioned view
- FIG. 11 shows a sixth exemplary embodiment of the invention in a schematic, partially sectioned view.
- FIG. 12 shows a seventh exemplary embodiment of the invention in a schematic, partially sectioned view.
- the torque transmission device 1 shows a first exemplary embodiment of a torque transmission device 1 according to the invention.
- the torque transmission device 1 has a part of an input shaft 10 of the torque transmission device, a first clutch device 12, a second clutch device 14, a transmission device 16 and an output shaft 18, which at the same time act as an output shaft of the transmission device 16 is designed.
- the input shaft 10 of the torque transmission device 1 is shown here as a crankshaft of a motor vehicle, which is driven by the cylinders 20 of a motor vehicle. stuff is loaded.
- the cylinders 20 are in particular cylinders of a motor vehicle drive device, such as an internal combustion engine.
- the first clutch device 12 and the second clutch device 14 are each designed as a friction clutch and in particular each have a stop 22, 24, a clutch disk and a pressure plate. Furthermore, the coupling devices 12, 14 have a common housing 34. This common housing is coupled on the drive side of the coupling devices 12, 14 in a rotationally fixed manner to the input shaft 10 of the torque transmission device 1.
- the drive side is to be understood as the side which faces the motor vehicle drive device within the drive train, while the drive side is to be understood as the side which faces a drive axle of the motor vehicle within the drive train.
- the first clutch device 12 is arranged on the drive side of the second clutch device 14.
- the first coupling device 12 and the second coupling device 14 each have a spring-damper device 36, 38.
- the spring-damper device 36, 38 is arranged essentially in the circumferential direction to the stop 22, 24 or to the clutch disc or to the pressure plate and in each case preferably has a plurality of spring elements which are spaced apart from one another in the circumferential direction.
- the output part 30 of the first clutch device 12 is non-rotatably connected to the first transmission input shaft 40, and the output part 32 of the second clutch device is non-rotatably coupled to a second transmission input shaft 42, which is a hollow shaft.
- the second transmission input shaft 42 can be very short in the axial direction.
- the first transmission input shaft 40 is coupled to the first shaft 46 via a transmission stage 44, by means of which the slow speed is translated
- the second transmission input shaft 42 is coupled to the second shaft 50 via a transmission stage 48, by means of which the slow speed is translated that a torque from the first transmission input shaft 40 to the first shaft 46 and from the second transmission input shaft 42 a torque can be transmitted to the second shaft 50.
- the translations of the translation stages 44, 48 are the same. Furthermore, with the same direction of rotation on the input side, these transmission stages 44, 48 each effect the same direction of rotation on the output side.
- the translation stage 44 and / or the translation stage 48 can, however, also be designed, which is not shown in FIG. 1, in such a way that this respective translation stage 44 or 48 translates quickly or 1: 1. Furthermore, the translation stages 44, 48 can be designed such that the translations of these translation stages 44, 48 are different. Furthermore, what is also not shown in FIG. 1, the translation stages 44, 48 can be designed in such a way that they cause a different output rotation direction with the same input rotation direction.
- the gear ratios 44, 48 are each shown as a pair of gears.
- the transmission stages 44, 48 can each be designed such that the transmission between the first transmission input shaft 40 and the first shaft 46 or the second transmission input shaft 42 and the second shaft 50 by arranging a plurality of intermeshing gear wheels or by means of a belt or belt is effected by means of friction wheels or in some other way.
- Four transmission stages are arranged between the first shaft 46 and the third shaft 18 or four transmission stages can be switched, namely the transmission stages 52, 54, 56, 58.
- Four transmission stages can be switched between the second shaft 50 and the third shaft 18 or four translation stages are arranged, namely the translation stages 60, 62, 64, 66.
- gear ratios are realized here by gear pairs or an arrangement of several gears.
- the translation stages can also be implemented in other ways.
- the translation stages 52, 54, 56, 58, 62, 64, 66 bring about the same direction of rotation of the third shaft 18 in the same direction of rotation of the first shaft 46 and the second shaft 50, which is achieved here in that these translation stages each by a Gear pair are formed.
- This translation stages 52, 54, 56, 58, 62, 64, '66 are, beginning with one, numbered consecutively in the direction of increasing translation with natural numbers. These natural numbers correspond in particular to the numbering of the forward gears which can be shifted with the torque transmission device 1 or the transmission device 16.
- the transmission stage 52 is the first gear
- the transmission stage 64 is the second gear
- the transmission stage 58 is the third gear
- the transmission stages 54 and 62 are the fourth gear
- the transmission stage 66 is the fifth gear and Gear ratio 56 assigned to sixth gear.
- the transmission stage 60 has three intermeshing gearwheels, a first of which is arranged on the second shaft 50, a second on an intermediate shaft and a third on the third shaft 18, the direction of rotation of the third being reversed with respect to the forward gears with the same direction of rotation of the second shaft 50 Wave 18 is effected.
- the reverse gear is assigned to the transmission stage 60. 1 shows only one gear stage 60, which is assigned a reverse gear. However, a plurality of gear ratios can also be provided, to which a reverse gear is assigned.
- the numbering of the gears in FIG. 1 is only determined by the translations of the gear ratios 52, 54, 56, 58, 62, 64, 66, since in FIG. 1 no further gear ratios are provided in the drive train, which have the effect that when each is closed Coupling devices and the same speed of the input shaft 10 a different speed of the first shaft 46 and the second shaft 50 is effected.
- the order of the gear ratios 52, 54, 56, 58, 62, 64, 68 according to the size corresponds to the order of the overall gear ratio between the input shaft 10 and the third shaft 18 or, which is not shown here, a predetermined one Drive axle of a motor vehicle with a torque transmission device 1. If necessary, further gear ratios would have to be taken into account when numbering the gears. if you have an influence on the respective overall gear ratios between the crankshaft 18 or a drive axle of the vehicle, not shown.
- the transmission stage 52 of the first gear has a gear 68 arranged on the third shaft 18 so that it cannot rotate, via which the third shaft 18 can also be loaded when the transmission stage 60 of the reverse gear is engaged or engaged, so that a transmission stage 52 of the first shaft and a step 60 of the second shaft act on the same gear 68 of the third shaft 18.
- the gearwheel 70 which is arranged on the third shaft 18 in a rotationally fixed manner, is loaded both when the transmission stage 54 of the fourth gear arranged between the first shaft 46 and the third shaft 18 is engaged or switched, as well as when the transmission stage 62 of the between the second shaft 50 and the third shaft 18 arranged gear ratio 62 of the fourth gear is inserted.
- the gear wheels 72, 74, 76, 78 are each assigned to only one gear ratio 64, 56, 66, 58.
- the gear wheels 80, 82, 84, 86 of the first, fourth, sixth and third gears are rotatably mounted on the first shaft 46.
- the gear wheels 88, 90, 92, 94 are rotatably mounted on the second shaft 50.
- the third clutch device 96 which is designed as a jaw clutch with a synchronization device, can be used to shift into first gear or into fourth gear.
- a rotationally fixed connection between the first shaft 46 and the gear 80 of the first gear or the first shaft 46 and the gear 82 of the fourth gear is generated.
- the third clutch device is arranged on the first shaft 46 between the gear 80 of the first gear and the gear 82 of the fourth gear.
- the sixth or third gear can be achieved by means of the clutch device 98, the reverse gear by means of the third clutch device 100 or the fourth gear and by means of the third clutch device 102 the second gear or the fifth gear.
- the third clutch devices 96, 98 can be switched independently of the third clutch devices 100, 102.
- the second gear is engaged, the third clutch device 102 producing a rotationally fixed connection between the gear 92 and the second shaft 50, and the second clutch device 14 being closed and thus transmitting a torque.
- the first clutch device 12 is essentially open and the third clutch device 96, 98, 100 are essentially completely open, so that they do not produce a rotationally fixed connection between a gearwheel of a transmission stage and the first shaft 46.
- a torque is transmitted from the direction of the motor vehicle drive direction via the input shaft 10, the second clutch device 14, the high shaft 42 and the transmission stage 48 to the second shaft 50, from which the torque via the third clutch device 102 and the transmission stage 64 to the third shaft 18, and from here in particular to the drive axles of the motor vehicle.
- the speed of the first shaft 46 is adapted or synchronized with the speed of the gear 68 of the gear ratio 58 of the third gear, in particular when the first clutch device 12 is open by means of the synchronization device or the synchronizer rings of the third clutch device 98 , As soon as the first shaft 46 and the gear 86 have the same speed, the dog clutch of the third clutch device is device 98 closed in such a way that the first shaft 46 is substantially non-rotatably connected to the gear 86 of the gear ratio 58 of the third gear.
- Closing the third clutch device thus rotates the first shaft 46, but the first clutch device 12 is initially still open.
- the first clutch device 12 is then increasingly closed, the second clutch device 14 being increasingly opened.
- This in particular has the effect that the proportion of the torque which, as described above, is transmitted from the input shaft 10 via the second shaft 50 to the third shaft 18, decreases, and instead torque increasingly increases via the input shaft 10, the first Coupling device 12, the first transmission input shaft 40 and the transmission stage 44 is transmitted to the first shaft 46 and is forwarded from there via the coupling device 98 and the transmission stage 58 of the third gear to the third shaft 18.
- the second clutch device 14 is opened completely.
- the first clutch device 12 synchronizes the input shaft 10 or the internal combustion engine to the speed of the new gear. This transfer from one of the clutch devices 12, 14 to the other of these clutch devices 12, 14 is referred to as an overlap circuit.
- the entire torque introduced by the input shaft 10 of the torque transmission device into the torque transmission device 1 is transmitted from this torque transmission device 1 to the output side, so that a load shift is given.
- FIG. 1 shows the torque transmission device in a simplified representation, in which the third clutch devices 110, 112, 114, 116, 118, 120, 122, 124 each have the transmission stages 52, 54, 56, 58, 60, 62, 64, 66 arranged on the output side are, so that here, in particular, the gearwheels arranged on the third shaft of the aforementioned transmission stages can be coupled to the third shaft or can be uncoupled from the third shaft.
- FIG. 3 to 5 illustrate, in approximation to FIG. 2, exemplary circuits which can be carried out with a torque transmission device according to the invention. It should be noted that in the representations according to FIGS. 3 to 5, the third coupling devices can also be designed in particular in the manner shown in FIG. 1.
- FIG. 3 illustrates in particular load shifts from the first to the second, from the second to the third, from the third to the fourth, from the fourth to the fifth and from the fifth to the sixth gear.
- the shifts from the first to the second, from the second to the third and from the fifth to the sixth gear are carried out essentially as has already been shown for a shift from the second to the third gear.
- a power shift from third to fourth gear is initially carried out in essentially the same way. However, as soon as the fourth gear is engaged between the second shaft and the third shaft, the fourth gear is additionally shifted or engaged between the first shaft 46 and the third shaft 18.
- the first clutch device 12 and the second clutch device 14 are in particular friction clutches. Mechanical locking is not to be feared if both fourth gears are engaged.
- the first 12 and the second clutch device 14 are essentially closed when both fourth gears are engaged.
- Non-uniformities can be compensated for, for example, by the spring-damper devices 36, 38.
- the second clutch device 14 and, preferably simultaneously, the third clutch device 124 via which the transmission stage 64 of the fourth gear between the second shaft 50 and the third shaft 18 has been switched open.
- the second shaft 50 is synchronized by means of the third clutch device 126 in accordance with the transmission stage 66 of the fifth gear, and then, as already described above, the claw clutch of the third clutch device 126 is closed. An overlap shift from gear 4 to gear 5 is then carried out.
- FIG. 4 shows a representation corresponding essentially to FIG. 3, on the basis of which the load shifts from the second to the fourth and from the fourth to the sixth gear are to be illustrated.
- the gear is shifted from the second gear or the gear ratio 62 essentially to the fourth gear or gear ratio 56, which is arranged between the first shaft 46 and the third shaft 18, as already described above with regard to a gearshift from the second into the third gear was shown
- This is realized by means of an overlap circuit.
- the third clutch device 114 is closed or as soon as the second clutch device 14 is opened, the third clutch device 124 is closed, wherein in particular synchronization is carried out in accordance with the above description.
- the second coupling device 14 is then closed again.
- the first clutch device 12 and the third clutch device 114 are opened.
- a shift with an overlap shift is then carried out, which essentially corresponds to the shifting process described above in relation to a shifting process from second to third gear.
- FIG. 5 shows an illustration of a transmission device according to the invention, which essentially corresponds to the illustration according to FIG. 2.
- FIG. 5 shows in particular a power shift from third to fifth gear. This shifting can be carried out in accordance with the shifting performed above with respect to a shift from second to third gear.
- Fig. 6 different switching operations of a 6-speed transmission are shown schematically, the combination of two numbers by a hyphen means that switching between the gears numbered with these numbers.
- the gearshifts not encircled in FIG. 6 can be shifted under load, while the circled gearshifts, i.e. the double gear shift 1-3 and the triple shift mechanisms 2-5 and 3-6 and the five-way circuit 1-6, with the embodiments according to FIGS. 1 to 5 are not executed under load.
- Fig. 6 simply means that a gear is shifted to a next higher or lower gear, double means that two gears are shifted up or two gears down, triple that three gears are shifted up or down, four times that directly four gears , shifted up or down, and five times that five gears are shifted up or down.
- the invention is not to be limited in particular by the embodiments according to FIGS. 1 to 5 to the extent that predetermined switching operations, namely those circled in FIG. 6, cannot be switched under load or with full torque transmission by the torque transmission device.
- the circuits 1-6 and 3-6 can be realized with a torque transmission device 1 according to FIG. 1 in that in addition a gear ratio, which has the gear ratio assigned to sixth gear or gear ratio 56, between the second shaft 50 and the third shaft 18 is arranged or can be switched.
- the possibility of shifting directly from second to fifth gear or vice versa can be realized in a torque transmission device according to one of FIGS. 1 to 5 in that a further gear ratio with a gear ratio which corresponds to the gear ratio of gear ratio 66 of the fifth gear, is arranged between the first shaft 46 and the third shaft 18.
- a circuit from first to third gear under load can be realized in a torque transmission device according to one of FIGS. 1 to 5 by additionally arranging a transmission stage between the second shaft 50 and the third shaft 18, the translation of which essentially corresponds to the translation of the translation. level 58 of the third gear corresponds.
- FIGS. 7 to 11 show torque transmission devices or double clutch transmissions which essentially correspond to the embodiment according to FIG. 1. The respective differences from FIG. 1 and between these embodiments according to FIGS. 7 to 11 are shown below:
- the embodiment according to FIG. 7 differs from the embodiment according to FIG. 1 essentially in that in FIG. 7 the ratios between the first transmission input shaft 40 and the first shaft 46 and the second transmission input shaft 42 and the second shaft 50 have been chosen differently , 7, in particular, the transmission ratio between the first transmission input shaft 40 and the first shaft 46 is 1: 1, or the first transmission input shaft and the first shaft in FIG. 7 are designed as a (one-piece) shaft.
- the third shaft 18 is not aligned concentrically with the first transmission input shaft 40.
- the embodiment according to FIG. 7 differs from the embodiment according to FIG. 1 in that the transmission ratio between the second transmission input shaft 42 and the second shaft 50 was chosen differently from FIG. 1.
- the embodiment of the invention shown in FIG. 8 differs from that in FIG Fig. 7 illustrated embodiment of the invention in that in Fig. 8 not the first shaft 46, but the second shaft 50 is concentrically aligned with the torque transmission device. 8, the second clutch device 14 is arranged on the transmission side of the first clutch device 12.
- the illustration according to FIG. 8 differs from the illustration according to FIG. 7 in that the second transmission input shaft 42 is arranged concentrically within the first transmission input shaft 40.
- the first transmission input shaft 40 is a hollow shaft in FIG. 8.
- a first actuator 180 having a driving means 182 for actuating the first clutch means 12, a second actuator 184 'of a second driving means 185 for actuating the second coupling means 14, and third actuators 188 , 190 with third drive devices 192, 194, 196, 198.
- the third actuating devices 180, 184, 188, 190 with third drive devices 182, 186, 192, 194, 196, 198 have ratios 200, 202, 204, 206.
- the third actuating devices 188, 190 are also essentially separate or independent of one another.
- the third actuation devices 188, 190 with a third drive device 192, 194 and 196, 198 are each designed similarly or identically.
- the third actuating devices 188 and 190 each have an electric motor 194 and 198, which can move an engagement element in such a way that this engagement element is switched in a switching position from which it is connected to a third clutch device 96 or 98 or 100 or 102 can be brought into engagement or from which this respective third coupling device can be switched.
- FIG. 10 shows an exemplary embodiment of the invention, which differs from the embodiment shown in FIG. 9 essentially by the third actuating devices 188, 190 and their drive devices 210, 212. Only one drive device 210 or 212 is provided for each first shaft 46 and for each second shaft 50. This drive device acts on a shift drum 214, 216, which may each have a gear ratio.
- the third clutch devices 96, 98 are actuated by means of the shift drum 214, while the third clutch devices 100, 102 are actuated by means of the shift drum 216.
- FIG. 11 differs from the embodiments of the invention shown in FIGS. 9 and 10 essentially in that an actuating device 220, 222, 224, 226 is provided per third coupling device 96, 98, 100, 102 which each have a drive device 228, 230, 232, 234. Translations 236, 238, 240, 242 are optionally provided within the actuating devices 220, 222, 224, 226.
- the exemplary embodiment of the invention shown in FIG. 12 differs from that in FIG. 1 essentially in that the first coupling device 12 and the second coupling device 14 are arranged on the driven side of the first shaft 46 and the second shaft 50, respectively.
- a fourth clutch device 260 is arranged between the input shaft 10 of the torque transmission device 1 and the third shaft 18, which is designed as a friction clutch and can couple the input shaft 10 to the third shaft 18 in a rotationally fixed manner or can decouple these shafts 10, 18. Furthermore, the fourth clutch device can be switched into an intermediate stage, in which this fourth clutch device 260 can transmit a predetermined, limited torque.
- the third shaft 18 is arranged on the input side of the second shaft 46 and the third shaft 50.
- the first 12 and second 14 clutch devices are provided, which are multi-plate clutches and can be actuated by an actuating device 180 or 184 with drive device 182, 186.
- the first clutch device 12 can couple a wheel 262, which is rotatably mounted on the first shaft 46 and is a gear wheel here, to the first shaft 46 in a rotationally fixed manner. If it is coupled to the first shaft 46, this wheel 262 transmits a torque to a wheel 264 of the transmission output shaft 268.
- the second clutch device can couple the wheel 270 rotatably mounted on the second shaft 50 to the second shaft 50 so that a torque can be transmitted between the second shaft 50 and the transmission output shaft 268 via the wheels 270, 264.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Mechanical Operated Clutches (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
Abstract
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2001237226A AU2001237226A1 (en) | 2000-02-15 | 2001-01-18 | Torque transmission device, in particular with double clutch drive mechanism |
GB0218638A GB2384036B (en) | 2000-02-15 | 2001-01-18 | Torque transmission device with double clutch transmission |
BR0108334-1A BR0108334A (pt) | 2000-02-15 | 2001-01-18 | Dispositivo de transmissão de torque, especialmente com transmissão de embreagem dupla |
KR1020027010518A KR20020079851A (ko) | 2000-02-15 | 2001-01-18 | 이중 클러치 트랜스미션을 갖는 토크 전달장치 |
JP2001560033A JP2003522922A (ja) | 2000-02-15 | 2001-01-18 | 特にダブルクラッチ伝動装置を備えたトルク伝達装置 |
DE10190518T DE10190518D2 (de) | 2000-02-15 | 2001-01-18 | Drehmomentübertragungsvorrichtung, insbesondere mit Doppelkupplungsgetriebe |
US10/223,055 US6755089B2 (en) | 2000-02-15 | 2002-08-15 | Torque transfer device more particularly with double clutch transmission |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10006562 | 2000-02-15 | ||
DE10006562.7 | 2000-02-15 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/223,055 Continuation US6755089B2 (en) | 2000-02-15 | 2002-08-15 | Torque transfer device more particularly with double clutch transmission |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2001061212A1 true WO2001061212A1 (de) | 2001-08-23 |
Family
ID=7630896
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2001/000217 WO2001061212A1 (de) | 2000-02-15 | 2001-01-18 | Drehmomentübertragungsvorrichtung, insbesondere mit doppelkupplungsgetriebe |
Country Status (12)
Country | Link |
---|---|
US (1) | US6755089B2 (de) |
JP (1) | JP2003522922A (de) |
KR (1) | KR20020079851A (de) |
CN (1) | CN1401060A (de) |
AU (1) | AU2001237226A1 (de) |
BR (1) | BR0108334A (de) |
DE (2) | DE10190518D2 (de) |
FR (1) | FR2805328B1 (de) |
GB (1) | GB2384036B (de) |
IT (1) | ITMI20010307A1 (de) |
RU (1) | RU2002124600A (de) |
WO (1) | WO2001061212A1 (de) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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-
2001
- 2001-01-18 WO PCT/DE2001/000217 patent/WO2001061212A1/de active Application Filing
- 2001-01-18 RU RU2002124600/11A patent/RU2002124600A/ru not_active Application Discontinuation
- 2001-01-18 DE DE10190518T patent/DE10190518D2/de not_active Expired - Fee Related
- 2001-01-18 CN CN01805013A patent/CN1401060A/zh active Pending
- 2001-01-18 DE DE2001102028 patent/DE10102028A1/de not_active Withdrawn
- 2001-01-18 GB GB0218638A patent/GB2384036B/en not_active Expired - Fee Related
- 2001-01-18 BR BR0108334-1A patent/BR0108334A/pt not_active IP Right Cessation
- 2001-01-18 JP JP2001560033A patent/JP2003522922A/ja active Pending
- 2001-01-18 AU AU2001237226A patent/AU2001237226A1/en not_active Abandoned
- 2001-01-18 KR KR1020027010518A patent/KR20020079851A/ko not_active Application Discontinuation
- 2001-02-14 IT IT2001MI000307A patent/ITMI20010307A1/it unknown
- 2001-02-14 FR FR0101983A patent/FR2805328B1/fr not_active Expired - Fee Related
-
2002
- 2002-08-15 US US10/223,055 patent/US6755089B2/en not_active Expired - Fee Related
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Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004217204A (ja) * | 2003-01-09 | 2004-08-05 | Luk Lamellen & Kupplungsbau Beteiligungs Kg | 全輪駆動のためのパラレルシフト伝動装置および前輪駆動車両に横置きするためのパラレルシフト伝動装置 |
EP1626207A3 (de) * | 2004-08-11 | 2010-03-17 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Doppelkupplungsgetriebe und Verfahren zu seiner Steuerung |
WO2008052739A1 (de) * | 2006-11-02 | 2008-05-08 | Daimler Ag | Doppelkupplungsgetriebe |
CN102927212A (zh) * | 2012-09-26 | 2013-02-13 | 杭州萧山江南通用机械厂 | 一种用于减速或增速的齿轮箱 |
RU2656809C1 (ru) * | 2017-09-28 | 2018-06-06 | Федеральное государственное унитарное предприятие "Центральный ордена Трудового Красного Знамени научно-исследовательский автомобильный и автомоторный институт "НАМИ" (ФГУП "НАМИ") | Устройство электрогидравлического управления двойным сцеплением и коробкой передач |
RU2775958C1 (ru) * | 2021-10-20 | 2022-07-12 | Российская Федерация, от имени которой выступает Министерство обороны РФ | Устройство управления трансмиссией |
Also Published As
Publication number | Publication date |
---|---|
US6755089B2 (en) | 2004-06-29 |
GB0218638D0 (en) | 2002-09-18 |
DE10102028A1 (de) | 2001-08-16 |
JP2003522922A (ja) | 2003-07-29 |
KR20020079851A (ko) | 2002-10-19 |
US20030051577A1 (en) | 2003-03-20 |
FR2805328A1 (fr) | 2001-08-24 |
GB2384036A (en) | 2003-07-16 |
CN1401060A (zh) | 2003-03-05 |
GB2384036B (en) | 2004-11-10 |
BR0108334A (pt) | 2003-03-11 |
AU2001237226A1 (en) | 2001-08-27 |
FR2805328B1 (fr) | 2003-05-16 |
ITMI20010307A1 (it) | 2002-08-14 |
RU2002124600A (ru) | 2004-02-10 |
DE10190518D2 (de) | 2003-02-20 |
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