WO2012034782A2 - Verteilergetriebe - Google Patents
Verteilergetriebe Download PDFInfo
- Publication number
- WO2012034782A2 WO2012034782A2 PCT/EP2011/063337 EP2011063337W WO2012034782A2 WO 2012034782 A2 WO2012034782 A2 WO 2012034782A2 EP 2011063337 W EP2011063337 W EP 2011063337W WO 2012034782 A2 WO2012034782 A2 WO 2012034782A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- shaft
- gear
- output shaft
- transfer case
- clutch
- 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
- B60K17/34—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
- B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential 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
- B60K17/34—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
- B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
- B60K17/3467—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear combined with a change speed gearing, e.g. range gear
-
- 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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
-
- 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
- Y10T74/19084—Spur
Definitions
- the invention relates to a transfer case for a drive of a continuously driven first wheel axle and at least one additional shiftable axle of a motor vehicle with an input shaft driven by a manual transmission and a coaxially extending to this first output shaft, which serves to drive the constantly driven wheel axle, with a countershaft to the input shaft and the first output shaft arranged intermediate shaft and with one of the intermediate shaft via a pair of wheels driven second output shaft which serves to drive the other switchable wheel axle, wherein the first output shaft is driven via a first clutch selectively with a direct transmission or a reduction.
- Motor vehicles are provided to improve their traction and in the context of increasing the maximum transmittable torque with multi-axis drives.
- all-terrain commercial vehicles, Trac vehicles and construction machinery come drive concepts with multiple driven axles are used in which all wheel axles are permanently or partially selectively switched on or switched off via a separate or flanged to the transmission housing transfer case.
- manufacturers of commercial vehicles which equip appropriate types of vehicles with both four-wheel drive and rear-wheel drive, it is of great importance that in both cases the overall design of the commercial vehicle is substantially identical.
- a goal is to maintain a low position of the cab of the commercial vehicle, even if it is equipped with an all-wheel drive.
- a transfer case of the type specified in the preamble of claim 1, which satisfies the above conditions for driving two axles, is known from DE 22 52 050 B2.
- This transfer case with an equiaxed arrangement of input shaft and first output shaft has, apart from a wave train for an outgoing on both sides of the transfer case power take-off, for the circuit in its idle or in two drive stages four more wave trains.
- the drive stages may have a direct transmission or translation and a reduction.
- a separate intermediate shaft receiving receiving shaft portion is inserted within the shaft train, which includes the input shaft and the first output shaft, said intermediate gear meshes with a freely rotatable on the one intermediate shaft and engageable with this gear and a ring gear of a differential gear.
- the structural dimensions of the transfer case should be reduced so that it can be easily accommodated within the space limited by the vehicle frame space.
- the first clutch is to be arranged directly on the input shaft and connect the input shaft directly to the first output shaft or a first driven gear arranged in a first switching position for direct transmission and it should connect the first clutch in a second switching position freely rotatably mounted on the input shaft rotatably mounted first drive wheel with this and drive the first output shaft via the formed on the intermediate shaft countershaft, whereby the first output shaft is driven at a reduced speed.
- the first clutch can take two different switching positions, where it connects the input shaft with the first output shaft for direct drive through or coupling to reduce the speed of the first output shaft relative to the rotational speed of the input shaft, the first drive wheel with the input shaft, so that the first output shaft in This off-road gear is powered by the countershaft.
- By providing a direct drive through the height of the transfer case based on the position of the input shaft can be reduced, so that the space for the arrangement of a driver's cab in commercial vehicles is not limited, ie, the car can take a relatively low position.
- the transfer case must be designed so that the universal drive shaft between the gearbox and the axle can be retained in a standard 4x2 truck.
- the transfer case has little misalignment with the rear axle, allowing the vehicle cab to remain low.
- a first clutch which alternately performs both functions
- two can be separated be provided mutually arranged clutches, one for the direct drive and one for fixing the first gear on the intermediate shaft or on a member of a differential gear.
- These separately arranged clutches may have opposite directions of actuation for their engagement process, so that they can be actuated alternately by means of a shift rod.
- the first clutch should be arranged directly on the input shaft and connect the input shaft directly to the first output shaft in an engaged switching position for direct transmission.
- a first drive wheel rotatably connected to the input shaft to be engaged with a first gear, which in a second range group corresponding to a terrain group, and in the case that there is no differential, via a third clutch to the intermediate shaft or to a member a differential gear can be coupled, wherein the first output shaft is driven via the formed on the intermediate shaft countershaft with reduced speed.
- a direct transmission means that the first output shaft is driven by the input shaft 1: 1.
- the first clutch is thus not designed as a double clutch, because instead of single clutches are provided between the input shaft and the first output shaft and between the first gear and the intermediate shaft or a member of the differential gear.
- the construction cost is substantially increased by the fact that there is no direct drive from the input shaft to the first output shaft. Rather, depending on the switching position of a clutch belonging to assembly B, the input shaft drives a first intermediate shaft with transmission or reduction. From this first intermediate shaft, a second intermediate shaft arranged differential gear via a further clutch and an intermediate driven. An output shaft of the differential gear drives then via another gear pair leading to the rear axle output shaft.
- the external dimensions of the transfer case are significantly increased by the use of four wave trains.
- a rotatably connected to a second drive wheel stub shaft may be arranged which is rotatably mounted in the intermediate shaft, wherein the drive wheel with a arranged on a second output shaft second output gear is engaged and the stub shaft via a second clutch with the intermediate shaft is detachable.
- the second clutch on the second output shaft to selectively connect the second output gear with this.
- the second clutch can be combined or replaced with or by a frictional or positive-locking element that limits the transmittable to the front axle torque.
- a differential gear should be arranged within the intermediate shaft, whose members are connected to both a first and a second gear and a second drive wheel, wherein the second drive wheel is arranged with a arranged on the second output shaft second driven gear in engagement.
- the differential Consequently, the gearbox assumes the function of a longitudinal differential in the off-road gear, in which a planetary gear train rotates completely or almost completely in the block during slip-free operation of the vehicle.
- the translations of the wheels chains are chosen so that, taking into account the tire circumferences in slip-free operation on the differential gear no speed differences, so no compensating movements occur.
- the possibility of forming the differential gear as Stirnradplanetentrieb which is arranged spatially between the first and the second gear.
- the Stirnradplanetentrieb has only small axial dimensions, which correspond substantially to those of the first clutch. This results in an extremely compact arrangement and thus a reduction in the axial length of the transfer case. It is advantageous if the members of the Stirnradplanetentriebes a web with the first gear, a ring gear with the second gear and a sun gear with the second drive wheel are connected.
- the differential gear blocking clutch between the web and the sun gear, which couples the first gear driven by the first drive gear with the second drive wheel at a direct transmission from the input shaft to the first output shaft.
- the differential gear can be locked by means of the lock-up clutch.
- This lock-up clutch is in the formation of the transfer case with Leksdif- arranged in the region in which in the previously explained version without longitudinal differential, the second clutch is to be provided.
- lock-up clutch may be combined or replaced by a frictional or positive-locking element that limits the transmittable to the front axle torque.
- the utility vehicle is to be provided with a power take-off shaft for driving separate devices, to connect them to the web and thereby pass them through the second gear.
- the web is thus connected on the one hand with the first gear and on the other hand with the shaft leading to the power take-off.
- the power take-off shaft can transmit torque when the ring gear is braked, with the first gear and the second drive wheel being decoupled from the sun gear.
- the rear axle is locked by a parking brake or parking brake positive or positive locking.
- the first clutch can be designed such that it serves only for engagement or disengagement of the direct drive through to the first output shaft, while between the web and the first gear, a further clutch is arranged.
- the first gear may be in engagement with a driven gear arranged on a power take-off shaft. Consequently, the PTO shaft is in the switched off-road group, ie in all-wheel drive, driven. This is the case when the vehicle is being towed. In both versions for the drive of the PTO shaft, this is in communication with the web of the differential gear. However, when the vehicle is towed, the bridge is driven as a summation shaft consisting of sun gear and ring gear from the front axle and the rear axle. As an alternative to these two versions, the speed of the ring gear could be transmitted to the PTO shaft. Both the clutches and the lock-up clutch should preferably be designed as jaw clutches. The corresponding jaw clutches may, if necessary, be provided with a synchronization. In addition, however, it is also possible to provide one or all clutches with frictional drivers.
- the second output shaft in a housing which is separate from a transfer case, wherein the housing is intended to be pivotable about a longitudinal central axis of the intermediate shaft and fixable in different positions on the transfer case.
- a drive flange of the second output shaft can be pivoted together with the housing into a position in which the propeller shaft connected thereto with respect to the position of the gearbox, a crankcase or an oil pan of the internal combustion engine and a Eintriebs in a Vorderachsgetriebe an optimal position occupies and is driven with the least possible diffraction angle.
- FIG. 1 Show it: a schematic representation of a first embodiment according to the invention of a transfer case, a schematic representation of a second embodiment, which corresponds with respect to the shaft assembly a section along line II - II in Fig. 3, a view of an end face of a transfer case with a pivotable, a second output shaft receiving housing , A schematic representation of a third embodiment of a transfer case with a first drive type of a PTO shaft and a schematic representation of a second drive mode of a PTO shaft.
- FIGs 1, 2, and 4, 1 denotes an input shaft of a transfer case, which is driven by a unspecified manual transmission of a vehicle preferably designed as a utility vehicle on a drive flange 1 a, preferably via a propeller shaft.
- the vehicle may also be an agricultural Trac vehicle or a construction machine.
- a first clutch 2 is arranged, via which the input shaft 1 is selectively coupled to a rotatably on a first output shaft 3 arranged first output gear 4 or a freely rotatable on the input shaft 1 first drive wheel 5.
- first output gear 4 and the input shaft 1 are coupled to each other via the first clutch 2, takes place from the input shaft 1 from a direct drive to the first output shaft 3, via an output flange 3a and preferably via a propeller shaft, not shown, with a constantly driven rear axle of the vehicle is connected.
- an intermediate shaft 6 is arranged in the countershaft. Part of this intermediate gear, in addition to the intermediate shaft 6, a first gear 7, which is in engagement with the first drive wheel 5, and a second gear 8, which meshes with the first output gear 4.
- the first gear 7 and the second gear 8 are directly fixedly connected to the intermediate shaft 6.
- the rear axle of the vehicle is driven in a speed range which corresponds to an operation of the vehicle in a road group of the shift stages which can be shifted in the manual transmission.
- An overdrive area selectable via the first shift clutch 2 in which the input shaft 1 drives the first output shaft 3 via the first drive gear 5, the first gear 7, the intermediate shaft 6, the second gear 8, and the first driven gear 4 corresponds to a land group.
- a non-illustrated drive axle which may be a front axle, can also be driven by the intermediate shaft 6.
- a second clutch 9 which is arranged on a freely rotatable guided in the intermediate shaft 6 stub shaft 10 and can couple with the first gear 7.
- the stub shaft 10 receives a rotatably mounted on it second drive wheel 1 1, which is also engaged with a second output shaft 12 rotatably on a second output gear 12b.
- This second output shaft 12 is connected via an output flange 12a with a propeller shaft leading to an axle drive of the front axle.
- a differential gear 13 designed as a spur gear train set is arranged within the intermediate shaft and serves as a longitudinal differential between the rear axle and the front axle in the switched off-road group and therefore in all-wheel drive mode.
- the second clutch ie, the second wheel axle is permanently driven in the field group.
- a lock-up clutch 14 is provided, by means of which a web 15 with a sun gear 16 is connectable.
- This sun gear 16 is connected via a second drive shaft 17 with the second drive wheel 1 1 in connection, which drives in accordance with FIG. 1 arranged on the second output shaft 12 driven gear 12b.
- a ring gear 18 is connected to the second gear 8 of the intermediate gear.
- FIG. 3 is an end view of a trained according to the scheme of FIG. 2 transfer case is shown.
- the transmission elements are enclosed by a transfer case 19 and a housing 20 pivotable relative thereto.
- the drive flange 1a is recognizable, in the lower region of the housing 20 of the output flange 12a connected to the front axle via a drive shaft.
- a centrally extending through the intermediate shaft axis of rotation 21 is designated by intersecting dotted lines.
- the housing 20 can be pivoted relative to the transfer case 19, wherein both housings 19 and 20 can be fixed in different positions to each other.
- a changed situation is indicated by a dashed line. This makes it possible to optimize the position of the output flange 12a in such a way that avoids a large flexion angle of the propeller shaft and this on the manual transmission and on
- Figs. 4 and 5 show embodiments of the invention, which are based on the solution according to FIGS. 1 and 2. These arrangements also include a differential gear 13 disposed between the first gear 7 and the second gear 8. The links of this differential gear 13, namely the land 15, the sun gear 16 and the ring gear 18 are in the same manner as in Fig. 2 with the shafts connected.
- the second drive wheel 1 by means of a third clutch 22 selectively coupled to the drive shaft 1 7 or uncoupled.
- a power take-off shaft 23 which is passed through the second gear 8 of the intermediate gear.
- This power take-off shaft 23, also called PTO, is used to drive external devices. It is at standstill of the vehicle, ie at festgebremster first output shaft 3 and with transmission of torque on the first clutch 2 on the first gear 7 and disengaged other clutches (lock clutch 14 and third clutch 22) realized.
- the ring gear 18 is supported via the corresponding gears 4 and 8 on the first output shaft 3. In this way, can be realized by a low construction cost associated change of the transfer case a power take-off.
- Fig. 5 shows an alternative solution, with which also a power take-off is created.
- a first clutch 2a and a third clutch 2b between the input shaft 1 and the first output shaft 3 and between the first gear 7 and the Bridge 15 arranged.
- the PTO shaft 24 can be driven.
Landscapes
- 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)
- Structure Of Transmissions (AREA)
- Arrangement Of Transmissions (AREA)
- Transmission Devices (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/821,406 US8784256B2 (en) | 2010-09-16 | 2011-08-03 | Power divider |
EP11738736.5A EP2616264B1 (de) | 2010-09-16 | 2011-08-03 | Verteilergetriebe |
KR1020137006620A KR20130132768A (ko) | 2010-09-16 | 2011-08-03 | 동력 분배 장치 |
CN201180044847.4A CN103118892B (zh) | 2010-09-16 | 2011-08-03 | 分动器 |
ZA2013/02570A ZA201302570B (en) | 2010-09-16 | 2013-04-10 | Power divider |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010040883.2 | 2010-09-16 | ||
DE102010040883A DE102010040883A1 (de) | 2010-09-16 | 2010-09-16 | Verteilergetriebe |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2012034782A2 true WO2012034782A2 (de) | 2012-03-22 |
WO2012034782A3 WO2012034782A3 (de) | 2012-08-16 |
Family
ID=44584144
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2011/063337 WO2012034782A2 (de) | 2010-09-16 | 2011-08-03 | Verteilergetriebe |
Country Status (7)
Country | Link |
---|---|
US (1) | US8784256B2 (de) |
EP (1) | EP2616264B1 (de) |
KR (1) | KR20130132768A (de) |
CN (1) | CN103118892B (de) |
DE (1) | DE102010040883A1 (de) |
WO (1) | WO2012034782A2 (de) |
ZA (1) | ZA201302570B (de) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014205227A1 (de) * | 2014-03-20 | 2015-09-24 | Zf Friedrichshafen Ag | Verteilergetriebe |
DE102014205229A1 (de) * | 2014-03-20 | 2015-09-24 | Zf Friedrichshafen Ag | Verteilergetriebe |
CN105365558A (zh) * | 2015-11-23 | 2016-03-02 | 云南玉溪汇龙科技有限公司 | 新型变速箱分动器 |
CN105345671B (zh) * | 2015-12-07 | 2017-06-09 | 重庆大江工业有限责任公司 | 一种地面抛丸机传动*** |
CN110431034A (zh) * | 2017-04-07 | 2019-11-08 | 优尼邦斯股份有限公司 | 传递器 |
DE102017127583A1 (de) | 2017-11-22 | 2019-05-23 | Man Truck & Bus Ag | Achsgetriebesystem |
CN112762144B (zh) * | 2020-12-25 | 2022-02-15 | 中国第一汽车股份有限公司 | 一种分动器装置及车辆 |
KR102622197B1 (ko) * | 2021-11-24 | 2024-01-09 | 현대트랜시스 주식회사 | 모듈형 액슬 조립체 |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2252050B2 (de) | 1972-10-24 | 1980-10-30 | Engesa - Engenheiros Especializados S.A., Santo Amaro, Sao Paulo (Brasilien) | Verteilergetriebe für Kraftfahrzeuge |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2805586A (en) * | 1952-05-14 | 1957-09-10 | Harry G Lucas | Transfer case application |
US3046813A (en) | 1958-02-26 | 1962-07-31 | Rockwell Standard Co | Transfer case with brake and power take-off |
US3269217A (en) * | 1963-09-06 | 1966-08-30 | Maurice O Hoitan | Transmission-differential unit |
DE1655918A1 (de) * | 1966-11-05 | 1970-01-08 | Zahnradfabrik Friedrichshafen | Getriebe fuer Kraftfahrzeuge |
US3753376A (en) * | 1971-02-09 | 1973-08-21 | Engesa Engenheiros Especializa | Transfer and differential reduction box for motor vehicles |
US3999447A (en) * | 1974-12-23 | 1976-12-28 | Borg-Warner Corporation | Offset drive transfer mechanism |
JPS5655055Y2 (de) * | 1976-05-13 | 1981-12-22 | ||
JPS5823253B2 (ja) * | 1978-04-20 | 1983-05-13 | トヨタ自動車株式会社 | 車両用動力分割装置 |
US4605084A (en) * | 1983-10-20 | 1986-08-12 | Harry W. Mayer | Constant mesh gear transmission |
US4559846A (en) | 1983-11-10 | 1985-12-24 | Dana Corporation | System for shifting a vehicle to two or four-wheel drive |
US5381766A (en) * | 1993-11-05 | 1995-01-17 | Sakita; Masami | Rotary piston engine |
US5704444A (en) * | 1995-12-11 | 1998-01-06 | Borg-Warner Automotive, Inc. | Adaptive vehicle drive system for extreme operating conditioning |
RU2160192C1 (ru) * | 1999-10-11 | 2000-12-10 | Кузнецов Владимир Иванович | Раздаточная коробка для транспортного средства |
CN2570086Y (zh) * | 2002-09-12 | 2003-09-03 | 新疆升晟股份有限公司 | 单个差速器的差速分动装置 |
CN2570543Y (zh) * | 2002-09-12 | 2003-09-03 | 新疆升晟股份有限公司 | 四轮差速分动装置 |
CN2570085Y (zh) * | 2002-09-12 | 2003-09-03 | 新疆升晟股份有限公司 | 无壳式差速器的差速分动装置 |
CN2772878Y (zh) * | 2005-02-22 | 2006-04-19 | 沈阳天菱机械有限责任公司 | 轴间差速分动箱 |
US8172712B2 (en) * | 2007-05-29 | 2012-05-08 | Chrysler Group Llc | Compact power transfer unit for transaxle applications |
US8499658B2 (en) * | 2011-08-18 | 2013-08-06 | Arvinmeritor Technology, Llc | Transfer case for a vehicle |
-
2010
- 2010-09-16 DE DE102010040883A patent/DE102010040883A1/de not_active Withdrawn
-
2011
- 2011-08-03 KR KR1020137006620A patent/KR20130132768A/ko active IP Right Grant
- 2011-08-03 EP EP11738736.5A patent/EP2616264B1/de not_active Not-in-force
- 2011-08-03 US US13/821,406 patent/US8784256B2/en not_active Expired - Fee Related
- 2011-08-03 WO PCT/EP2011/063337 patent/WO2012034782A2/de active Application Filing
- 2011-08-03 CN CN201180044847.4A patent/CN103118892B/zh not_active Expired - Fee Related
-
2013
- 2013-04-10 ZA ZA2013/02570A patent/ZA201302570B/en unknown
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2252050B2 (de) | 1972-10-24 | 1980-10-30 | Engesa - Engenheiros Especializados S.A., Santo Amaro, Sao Paulo (Brasilien) | Verteilergetriebe für Kraftfahrzeuge |
Also Published As
Publication number | Publication date |
---|---|
KR20130132768A (ko) | 2013-12-05 |
CN103118892B (zh) | 2015-12-02 |
EP2616264A2 (de) | 2013-07-24 |
WO2012034782A3 (de) | 2012-08-16 |
US20130178324A1 (en) | 2013-07-11 |
US8784256B2 (en) | 2014-07-22 |
DE102010040883A1 (de) | 2012-03-22 |
EP2616264B1 (de) | 2014-06-25 |
ZA201302570B (en) | 2013-12-23 |
CN103118892A (zh) | 2013-05-22 |
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