WO2013045193A1 - Verteilergetriebe - Google Patents
Verteilergetriebe Download PDFInfo
- Publication number
- WO2013045193A1 WO2013045193A1 PCT/EP2012/066786 EP2012066786W WO2013045193A1 WO 2013045193 A1 WO2013045193 A1 WO 2013045193A1 EP 2012066786 W EP2012066786 W EP 2012066786W WO 2013045193 A1 WO2013045193 A1 WO 2013045193A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- gear
- drive
- extension
- transfer case
- input shaft
- Prior art date
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/22—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of main drive shafting, e.g. cardan shaft
- B60K17/24—Arrangements of mountings for shafting
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/342—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a longitudinal, endless element, e.g. belt or chain, for transmitting drive to wheels
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/348—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed
- B60K17/35—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed including arrangements for suppressing or influencing the power transfer, e.g. viscous clutches
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
-
- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
- F16H2057/02052—Axle units; Transfer casings for four wheel drive
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19023—Plural power paths to and/or from gearing
- Y10T74/19074—Single drive plural driven
- Y10T74/19079—Parallel
-
- 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
- Y10T74/19023—Plural power paths to and/or from gearing
- Y10T74/19074—Single drive plural driven
- Y10T74/19079—Parallel
- Y10T74/19102—Belt or chain
Definitions
- the present invention relates to a transfer case for distributing a drive torque of a drive unit of a motor vehicle to a first axis and a second axis of the motor vehicle.
- Transfer cases are transmissions for dividing a drive torque generated by the drive unit of the motor vehicle into several output drives. Typically find such Verteilerge gear in motor vehicles with permanent or switchable all-wheel drive application. They distribute the torque generated by the drive unit on two driven axles of the vehicle, the distribution depending on the design of the transfer case is predetermined or can be freely selected.
- a coupling unit is provided, for example, which offers the driver of the motor vehicle the option of switching between a permanent two-wheel drive mode in which the vehicle is driven exclusively via a primary axis an automatic four-wheel drive mode - a so-called "on-demand drive mode" - to choose. In this mode, depending on the driving conditions, some of the drive torque is transmitted to the wheels of the other axle (secondary axle) to provide temporary four-wheel drive.
- the transfer case can also be designed as a controllable center differential, in which a coupling unit is provided in order to set the distribution of drive torque in the longitudinal direction of the vehicle.
- a coupling unit is provided in order to set the distribution of drive torque in the longitudinal direction of the vehicle.
- the transfer case comprises a housing, an input shaft for introducing driving torque in the transfer case and a first output shaft for outputting drive torque to the first axis of the motor vehicle and a second output shaft for Outputting drive torque to the second axis of the motor vehicle, wherein the second output shaft is offset in parallel with respect to the input shaft.
- the transfer case includes an offset drive for transmitting drive torque from the input shaft to the second output shaft, the offset drive comprising a gear coaxial with the input shaft or the first output shaft.
- the gear is rotatably mounted on a portion of the housing of the transfer case.
- a reliable storage of the gear is ensured, which also can be implemented in a structurally simple and cost-effective manner.
- the rotational speed difference to be absorbed by the bearing - i. the speed difference between the gear and the component storing the gear - is the maximum speed of the gear.
- the mounting of the toothed wheel on the housing is advantageous, in particular in embodiments of the transfer case, in which the toothed wheel has a Includes recess through which the input shaft or the first output shaft extends coaxially.
- the toothed wheel has a Includes recess through which the input shaft or the first output shaft extends coaxially.
- the speed differences occurring are limited by the structure of the transfer case described above, which is why the storage can be designed according to simpler.
- lower efficiency losses of the Verteilergetrie- bes result.
- the first output shaft is permanently drivingly connected to the input shaft (e.g., connection via a differential, fixed connection or one-piece design).
- the second output shaft of the transfer case may basically be permanently operatively connected to the input shaft (e.g., via a differential gear).
- the transfer case comprises a coupling unit, by means of which the second output shaft is selectively decoupled from the input shaft.
- the housing portion which supports the gearwheel is an extension which is sleeve-shaped at least in sections and which surrounds the input shaft or the first output shaft at least in sections.
- the extension extends at least partially into the recess of the gear.
- the extension may be arranged at least in sections between the gear and the input shaft or the first output shaft.
- the extension is formed separately from the other portions of the housing. Especially the extension can be releasably secured to the housing of the transfer case, in particular screwed to this.
- such an extension-whether detachably attached to the housing or inseparably connected thereto- may be at least partially designed as a sleeve which surrounds the input shaft or the first output shaft and on which the toothed wheel is mounted.
- said housing portion (in particular said extension) surrounds the input shaft or the first output shaft without contact.
- no separate bearing is provided between said extension and the input shaft or first output shaft.
- An efficient bearing of the toothed wheel can be provided by arranging a roller bearing, preferably a radial bearing, in particular a needle roller bearing, between the toothed wheel and said housing section (in particular the extension mentioned).
- Rolling elements of the radial bearing cooperates, wherein the bearing surface is preferably a hardened portion of the extension.
- the bearing surface of the extension acts as a component of the rolling bearing.
- the outside arrangement of the bearing surface allows a comparatively simple processing of the extension in this area.
- the extension is hardened in the region of the bearing surface.
- the extension itself forms the bearing inner ring, so that the number of installed components is reduced and space is also saved.
- the assembly of the transfer case is simplified if the extension is accurately mounted on the housing by means of a centering device.
- the centering device comprises at least one guide element formed on the extension, which cooperates with at least one complementary configured and formed on the housing centering. Subsequently or simultaneously, the extension can be screwed to the housing, for example screwed, that is releasably secured.
- the extension may also be advantageous to fix the extension permanently to the housing, for example by welding or a shrink fit connection, or to form it integrally with the housing.
- a further simplification of the assembly of the extension results when the housing has a mounting collar on which said extension can be fastened. Since the mounting collar enhances the stability of the housing, it can also be used to support the input shaft or the first output shaft. It can be provided that the gear is supported in the axial direction on the extension.
- the extension can, for example, have an integral collar or flange with it. An axial support can for example also take place via a snap ring which can be fastened to the extension.
- Said gear may for example be a sprocket, if said offset drive forms a chain drive.
- the gear is part of a gear drive, wherein the gear in this case is connected via an intermediate gear drivingly connected to an output gear of the gear drive.
- the invention further relates to a drive train with a transfer case according to at least one of the embodiments described above, wherein the transfer case comprises a clutch unit through which the second output shaft is selectively acted upon by drive torque and wherein the drive train between the clutch unit of the transfer case and at least one wheel of the motor vehicle arranged further clutch for stopping a lying between the coupling unit and the coupling portion of the drive train comprises.
- the second axle of the motor vehicle or at least one wheel of the second axle can be separated from the rest of the drive train by the further clutch, so that said section of the drive train is shut down when the clutch unit and further clutch are open.
- An immobilizer drive train section can be provided for example in a motor vehicle with a permanently driven primary axis and an optionally driven secondary axis.
- a friction clutch can be arranged in the transfer case between the input shaft and the offset drive, and a suitable separating clutch (positive clutch or likewise friction clutch) in the region of an axle differential of the secondary axle.
- a drive train with a nonrigid drive train section is known, for example, from DE 10 2009 005 378 A1.
- the above-mentioned problem arises that despite the decommissioning of a part of the drive train, movable parts in the distributor transmission have comparatively large speed differences.
- the bearing of the said gear wheel of the offset drive is only claimed if the second output shaft is actually supplied with drive torque.
- the gear does not move and there is no speed difference between the gear and the gear bearing portion of the housing before.
- Fig. 1 is a schematic view of a drive train of a
- FIG. 2 is a schematic view of a transfer case
- 3 is a cross-sectional view of a transfer case of conventional design
- FIG. 5 perspective views of the gear of the offset drive of the transfer case overlapping extension.
- Fig. 1 shows schematically a drive train of a motor vehicle with shiftable four-wheel drive.
- the drive torque generated by a motor 1 1 - for example, an internal combustion engine or an electric motor (conceivable is also an arbitrarily ausgestalteter hybrid drive) - is supplied via a main gear 13 - for example, a manual transmission or an automatic transmission - a transfer case 15.
- a first output of the transfer case 15 is coupled via a propeller shaft 17 with a rear differential gear 19.
- wheels 21 of a rear axle 23 of the motor vehicle are permanently driven.
- the rear axle 23 thus forms the primary axis of the vehicle.
- a second output of the transfer case 15 is coupled via a propeller shaft 25 with a front axle Differentialge gear 27.
- a part of the drive torque of the motor 1 1 can be optionally transmitted to the wheels 29 of a front axle 31.
- the front axle 31 thus forms the secondary axle of the vehicle.
- a clutch 63 is provided, whose function will be explained in more detail below.
- Fig. 2 shows a schematic view of the transfer case 15 of FIG. 1.
- the transfer case 15 has an input shaft 41, a first output shaft 43 and a second output shaft 45.
- the first output shaft 43 is coaxial with the input shaft 41 and is rotatable with this - preferably in one piece - trained.
- the output shaft 45 is arranged offset parallel to the input shaft 41.
- the transfer case 15 further comprises a clutch unit 47 with a friction clutch 49 and an actuator 51.
- the friction clutch 49 has a clutch cage 53 which is non-rotatably connected to the input shaft 41 and the first output shaft 43 and carries a plurality of clutch plates. Furthermore, the friction clutch 49 has a rotatably mounted clutch hub 55, which also carries a plurality of clutch plates, which engage in an alternate arrangement in the lamellae of the clutch basket 53.
- the clutch hub 55 is rotatably connected to a drive gear 57 of a chain drive 59.
- An output gear 61 of the chain drive 59 is rotatably connected to the second output shaft 45.
- a gear drive may be provided, for example, with an intermediate gear between see the said gears 57, 61.
- the hub 55 in deviation from the illustrated construction in rotation with the shafts 41, 43 may be connected.
- the clutch basket 53 is in rotationally fixed connection with the drive gear 57. It is understood that the actuator 51 should then be arranged expediently different than shown.
- the clutch 63 is, for example, a dog clutch. It can be provided that the coupling 63 is assigned its own control unit. In many cases, however, it is advantageous if the coupling unit 47 and the clutch 63 are actuated by a common control unit.
- Fig. 3 shows details of a transfer case 15 'of conventional design in a cross-sectional view.
- the actuator 51 has a support ring 64 and an adjusting ring 65, which are rotatably mounted with respect to a rotation axis A of the input shaft 41 and the first output shaft 43.
- the support ring 64 is axially supported by a thrust bearing on the drive gear 57.
- the adjusting ring 65 is mounted axially displaceable.
- each have a plurality of ball grooves 67 and 69th These extend with respect to the axis A in the circumferential direction and are ramped with respect to a normal plane to the axis A in the circumferential direction, ie the ball grooves 67, 69 have in the circumferential direction a varying depth.
- a ball groove 67 of the support ring 64 and a ball groove 69 of the adjusting ring 65 are opposite each other and enclose In this case, an associated ball 71 can be provided.
- a respective actuating lever 77 and 79 is integrally formed on the support ring 64 and the adjusting ring 65.
- a respective roller 83 rotatably mounted (only the roller 83 of the lever 79 can be seen in Fig. 3).
- the actuating lever 77, 79 cooperate with the two end faces 87 of a control disk 89 which is rotatable relative to an axis C.
- the end faces 87 have a circumferential course with respect to a normal plane to the axis C, d. H. the control disk 89 is wedge-shaped in cross-section.
- control disk 89 By rotating the control disk 89, the actuating lever 77, 79 thus be moved like a scissor to rotate the support ring 64 and the adjusting ring 65 relative to each other.
- the control disk 89 has an integrally formed splined lug 91. Via this, the control disk 89 can be connected to an electric motor and an associated reduction gear drive-effective (not shown in Fig. 3).
- control disk 89 can be driven by appropriate control of said electric motor to a rotational movement, thereby pivoting the actuating lever 77, 79 relative to each other.
- the rotation of the support ring 64 and the adjusting ring 65 caused thereby relative to each other causes an axial movement of the adjusting ring 65.
- the pressure ring 73 thus causes an engagement of the friction coupling 49 or - supported by the plate spring assembly 75 - a disengagement of the friction clutch 49th
- the drive gear 57 is supported by a radial bearing 93 on the input shaft 41.
- the radial bearing 93 must accommodate the speed differences present between the components 41, 57.
- extension 95 is screwed to a mounting collar 97 of a housing 99 of the transfer case 15.
- the extension 95 can therefore be made as a separate component and is attached to the housing 99 only during assembly of the transfer case 15. Alternatively, it is also possible to form the extension 95 in one piece with the housing 99.
- the extension 95 extends into a gap between the input shaft 41 and a radial inner side of a recess 96 of the drive gear 57.
- the extension 95 is designed so that it does not touch the input shaft 41 in order to minimize friction losses. In special cases, it may be provided that between the extension 95 and the input shaft 41 is provided an additional radial bearing. In the illustrated embodiment, however, the input shaft 41 is supported in the illustrated recess by a bearing 101 in the housing 99.
- the bearing 101 is arranged in the region of the mounting collar 97.
- the mounting collar 97 therefore not only serves to attach the extension 95, but also provides a reinforced area of the housing 99 that allows reliable mounting of the input shaft 41.
- rolling elements of the radial bearing 93 are arranged, which is in particular a needle bearing. Since the bearing surface 103 is hardened, the rolling elements of the radial bearing 93 can be directly in contact with the extension 95.
- this also serves as a bearing surface.
- the bearing surface 103 and the inside of the recess 96 of the drive gear 57 thus act as a bearing inner ring or bearing outer ring of the radial bearing 93, which facilitates assembly and minimizes the number of components required.
- the drive gear 57 radially inwardly a recess 1 19, which is bounded laterally by extending in the radial direction webs 1 19a, 1 19b.
- the gear 57 is supported to the left via a thrust washer 1 17 on a flange portion 105 of the extension 95, which in turn is connected to the mounting collar 97.
- the drive gear 57 is supported on a snap ring 107 attached to the extension 95.
- the drive gear 57 is a sprocket of a chain drive 59.
- the drive gear 57 is - deviating from the construction of the transfer case 15' - with the clutch cage 53rd a friction clutch 49 of a coupling unit 47 in conjunction.
- the type of connection between the drive gear 57 and the coupling unit 47 can be freely designed as required.
- Fig. 5 shows perspective views of the extension 95. This has fastening segments 109, by means of which the extension 95 can be secured to the housing 99.
- the attachment segments 109 extend radially outward from the flange portion 105.
- the flange portion 105 defines a recess 1 1 1, which is formed complementary to the mounting collar 97 to ensure a snug fit of the extension 95 to the housing 99.
- At the mounting collar 97 and the flange portion 105 may complementary trained guide elements - for example, guide lugs and complementary guide grooves - be designed to facilitate the assembly of the extension 95.
- a hollow cylindrical bearing portion 1 13 which surrounds the input shaft 41 in the assembled state sleeve-like and non-contact and the radial outer side is provided for supporting the drive gear 57 with the bearing surface 103.
- a groove 1 15 At the end facing away from the flange portion 105 of the bearing portion 1 13 is provided with a groove 1 15 for receiving the snap ring 107.
- the storage of the drive gear 57 on the extension 95 and thus ultimately on the housing 99 causes at a decommissioning of the Drive gear 57 associated with the drive train no loss moments in the transfer case 15 occur.
- the input shaft 41 is not loaded by bending moments generated by the chain drive 59 provided to overcome the parallel offset between the rotation axis A of the input shaft 41 and a rotation axis B of the second output shaft 45. In fact, these bending moments would be transmitted to the latter on storage of the drive gear 57 on the input shaft 41, which would have to be taken into account in their design.
- the input shaft 41 and the components that support it eg the bearing 101
- the input shaft 41 and the components that support it can be made smaller since the bending moments mentioned are absorbed by the extension 95-and thus ultimately by the housing 99.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- General Engineering & Computer Science (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
- Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020147008153A KR101613803B1 (ko) | 2011-10-01 | 2012-08-29 | 트랜스퍼 케이스 |
US14/347,029 US9333855B2 (en) | 2011-10-01 | 2012-08-29 | Transfer case |
CN201280048445.6A CN103842200B (zh) | 2011-10-01 | 2012-08-29 | 分动器 |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011114788.1 | 2011-10-01 | ||
DE102011114788 | 2011-10-01 | ||
DE102011116143.4 | 2011-10-15 | ||
DE201110116143 DE102011116143B4 (de) | 2011-10-15 | 2011-10-15 | Verteilergetriebe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2013045193A1 true WO2013045193A1 (de) | 2013-04-04 |
Family
ID=46754999
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2012/066786 WO2013045193A1 (de) | 2011-10-01 | 2012-08-29 | Verteilergetriebe |
Country Status (4)
Country | Link |
---|---|
US (1) | US9333855B2 (de) |
KR (1) | KR101613803B1 (de) |
CN (1) | CN103842200B (de) |
WO (1) | WO2013045193A1 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015216497A1 (de) | 2015-08-28 | 2017-03-02 | Magna powertrain gmbh & co kg | Verteilergetriebe mit einem Zugmittel-Versatzgetriebe |
JP6233381B2 (ja) * | 2015-10-26 | 2017-11-22 | トヨタ自動車株式会社 | 4輪駆動車両用トランスファ |
DE102016112426A1 (de) * | 2016-07-06 | 2018-01-11 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Elektromotoranordnung und Verfahren zur Montage einer Elektromotoranordnung |
DE102016218731B4 (de) * | 2016-09-28 | 2021-09-30 | Audi Ag | Achsgetriebe für ein Kraftfahrzeug |
JPWO2020230829A1 (ja) * | 2019-05-13 | 2021-11-25 | 株式会社アイシン | 車両用電動駆動装置 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
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US4119168A (en) * | 1975-08-11 | 1978-10-10 | Borg-Warner Corporation | Automatic four-wheel drive transfer case |
EP0193704A1 (de) * | 1985-03-02 | 1986-09-10 | Dr.Ing.h.c. F. Porsche Aktiengesellschaft | Allradantrieb für ein Kraftfahrzeug |
DE10160026A1 (de) * | 2001-12-06 | 2003-06-26 | Gkn Automotive Gmbh | Betätigungsmechanismus zur Axialverstellung mit doppelter Funktion |
DE102004052870A1 (de) * | 2003-11-12 | 2005-06-23 | Ford Global Technologies, LLC, Dearborn | Schaltgetriebe und Verteilergetriebe mit integrierten Schmiersystemen |
WO2006128533A1 (de) * | 2005-04-28 | 2006-12-07 | Magna Powertrain Ag & Co. Kg | Verteilergetriebe für kraftfahrzeuge mit einer gesteuerten reibungskupplung |
US20070023249A1 (en) * | 2005-07-29 | 2007-02-01 | Magna Powertrain Ag & Co Kg | All-wheel transmission system |
DE102009005378A1 (de) | 2008-10-13 | 2010-04-15 | Magna Powertrain Ag & Co Kg | Antriebsstrang für ein Kraftfahrzeug |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
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US4447194A (en) | 1981-07-21 | 1984-05-08 | Lucas Industries Plc | Method of manufacturing a fuel pump |
US4848508A (en) | 1987-10-05 | 1989-07-18 | Borg-Warner Automotive, Inc. | Method and apparatus for controlling wheel slip in a full-time four wheel drive vehicle |
US5827145A (en) * | 1997-03-17 | 1998-10-27 | Asha Corporation | Hydraulic coupling having supplemental actuation |
US6589128B2 (en) * | 2001-11-02 | 2003-07-08 | New Ventures Gear, Inc. | On-demand two-speed transfer case for four-wheel drive hybrid vehicle |
US6638195B2 (en) | 2002-02-27 | 2003-10-28 | New Venture Gear, Inc. | Hybrid vehicle system |
US20060025267A1 (en) * | 2004-07-29 | 2006-02-02 | Mircea Gradu | Differential with torque vectoring capabilities |
DE102008032475A1 (de) | 2008-07-10 | 2010-01-14 | Magna Powertrain Ag & Co Kg | Verfahren zum Kalibrieren einer Kupplungseinheit |
-
2012
- 2012-08-29 US US14/347,029 patent/US9333855B2/en active Active
- 2012-08-29 CN CN201280048445.6A patent/CN103842200B/zh not_active Expired - Fee Related
- 2012-08-29 KR KR1020147008153A patent/KR101613803B1/ko active IP Right Grant
- 2012-08-29 WO PCT/EP2012/066786 patent/WO2013045193A1/de active Application Filing
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4119168A (en) * | 1975-08-11 | 1978-10-10 | Borg-Warner Corporation | Automatic four-wheel drive transfer case |
EP0193704A1 (de) * | 1985-03-02 | 1986-09-10 | Dr.Ing.h.c. F. Porsche Aktiengesellschaft | Allradantrieb für ein Kraftfahrzeug |
DE10160026A1 (de) * | 2001-12-06 | 2003-06-26 | Gkn Automotive Gmbh | Betätigungsmechanismus zur Axialverstellung mit doppelter Funktion |
DE102004052870A1 (de) * | 2003-11-12 | 2005-06-23 | Ford Global Technologies, LLC, Dearborn | Schaltgetriebe und Verteilergetriebe mit integrierten Schmiersystemen |
WO2006128533A1 (de) * | 2005-04-28 | 2006-12-07 | Magna Powertrain Ag & Co. Kg | Verteilergetriebe für kraftfahrzeuge mit einer gesteuerten reibungskupplung |
US20070023249A1 (en) * | 2005-07-29 | 2007-02-01 | Magna Powertrain Ag & Co Kg | All-wheel transmission system |
DE102009005378A1 (de) | 2008-10-13 | 2010-04-15 | Magna Powertrain Ag & Co Kg | Antriebsstrang für ein Kraftfahrzeug |
Also Published As
Publication number | Publication date |
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US20150040721A1 (en) | 2015-02-12 |
CN103842200A (zh) | 2014-06-04 |
US9333855B2 (en) | 2016-05-10 |
CN103842200B (zh) | 2016-06-29 |
KR20140056367A (ko) | 2014-05-09 |
KR101613803B1 (ko) | 2016-04-19 |
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