EP1047874B1 - Elektrische maschine mit getriebe - Google Patents

Elektrische maschine mit getriebe Download PDF

Info

Publication number
EP1047874B1
EP1047874B1 EP99963199A EP99963199A EP1047874B1 EP 1047874 B1 EP1047874 B1 EP 1047874B1 EP 99963199 A EP99963199 A EP 99963199A EP 99963199 A EP99963199 A EP 99963199A EP 1047874 B1 EP1047874 B1 EP 1047874B1
Authority
EP
European Patent Office
Prior art keywords
electrical machine
machine according
braking
braking devices
gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP99963199A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1047874A1 (de
Inventor
Martin-Peter Bolz
Ferdinand Grob
Stefan Tumback
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19927521A external-priority patent/DE19927521C2/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1047874A1 publication Critical patent/EP1047874A1/de
Application granted granted Critical
Publication of EP1047874B1 publication Critical patent/EP1047874B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N11/00—Starting of engines by means of electric motors
    • F02N11/04—Starting of engines by means of electric motors the motors being associated with current generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
    • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
    • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
    • F02N15/043—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer
    • F02N15/046—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer of the planetary type

Definitions

  • the present invention relates to an electrical machine used as a starter and generator for an internal combustion engine, in particular an internal combustion engine of a motor vehicle is switchable.
  • Such machines are has been developed as it enables the two functions of tempering the internal combustion engine and the generation of electric current, which is used for the vehicle's on-board systems, such as ignition, lighting etc. will unite in a single electrical machine and so weight and save costs.
  • An electrical machine with the features of the preamble of the claim 1 is known from DE-A-2504867.
  • the well-known electrical machine serves not only as a starter for the internal combustion engine and as a generator for the power supply of the motor vehicle, but serves in engine operation at the same time as a second drive unit for the motor vehicle.
  • the machine has one connected to the ring gear of a stage of the planetary gear Output shaft on while the output shaft of the internal combustion engine is connected to the central or sun gear of the other stage.
  • an electrical Machine for use as a starter or generator for an internal combustion engine created a simple switch between at the Operation of the electrical machine as a starter or as a generator optimally adapted Translation ratios allowed with simple means.
  • Desirable gear ratios are, for example, when used a claw pole machine (synchronous or asynchronous machine) as electrical Machine a gear ratio range from 1.6 to 4 for generator operation or from 4 to 60 in starter mode.
  • the spread, i.e. the ratio of the gear ratios to one another must be at least 2.
  • the braking force can in particular be attacked by the braking devices exercised on a ring gear of the planetary gear in a simple manner be, as braking devices in particular shoe brakes, multi-disc brakes or friction band brakes.
  • the construction according to the invention also enables a particularly compact design, in which the dimensions of the two ring gears are identical are. This reduces the number of different components required of the transmission and enables more rational and cost-effective production.
  • a common actuator to operate both brake devices provided the at least one working position, in the first brake device open and the second is closed, a working position in which the second brake device open and the first closed and has an idle position, in which both are open.
  • These positions are by one that is movable with one degree of freedom Control adjustable.
  • This degree of freedom is preferably a rotation so that the actuator for example with the help of any common Electric motors is easy to operate.
  • the actuator beyond a working position into a braking position is movable in the in the working position open braking device is braked.
  • the whole Closing a braking device should be the actuator only allow if not at the same time the other braking device is also closed is.
  • the Actuator in which the braking devices due to actuating movements parallel to an axis of the transmission are actuated, includes the actuator two ramps rotatable about this axis Converting a rotary movement into an actuating movement the braking devices. To operate the braking devices to couple, it is enough if the two Ramps are non-rotatably connected.
  • Such an actuator is especially for use with multi-disc brakes suitable as braking devices.
  • the adjusting device has at least a cam and with the cam interactive levers for implementing a rotation the cam disc in an actuating movement of the braking devices on.
  • the cam interactive levers for implementing a rotation the cam disc in an actuating movement of the braking devices on.
  • This configuration is particularly related to use with shoe brakes suitable as braking devices.
  • This drive train comprises an internal combustion engine 30 which can be connected via a main clutch 31 to a manual transmission 32 which drives various wheels of the motor vehicle with various adjustable transmission ratios via an output shaft 37.
  • An internal combustion engine shaft 4 passes through the manual transmission 32 and is connected to the transmission 33 of the electrical machine according to the invention.
  • the gear 33 has two stages, each gear stage 34 i , 34 ii is assigned its own braking device 35 i , 35 ii . With the aid of the braking devices, the transmission ratio between the shaft 4 and a shaft 6, which is connected to an electrical machine 36, can be adjusted.
  • One of the two transmission ratios of the transmission 33 is provided for the operation of the electrical machine 36 as a starter of the internal combustion engine 30 and the other for the operation as an alternator.
  • Figures 1 to 3 show highly schematic axial cuts through gears.
  • Short horizontal lines 10 represent each the toothing of a gear.
  • Two each such lines are indicated by a vertical line 11 connected, which symbolizes the disc of the gear.
  • An open circle 12 in the middle of the line 11 indicates that the gear in question by one Axis through a horizontal, through the circle 12 running line is symbolized, freely rotatable is.
  • a closed round point 13 represents one firm connection between the gear in question and its axis.
  • the internal combustion engine is coupled via a shaft 4 to a planet carrier 5, which rotatably holds planet wheels 2 1 , 2 2 of the two stages of the planetary gear.
  • These planet gears each mesh with a sun gear 1 i or 1 ii and a ring gear 3 i or 3 ii .
  • the sun gears are fixedly mounted on a shaft 6 coupled to the electrical machine (not shown).
  • a braking device (not shown in FIG. 1) engages on an outer surface 8 i , 8 ii of one of the ring gears 3 i , 3 ii and prevents it from rotating while the other ring gear is freely movable.
  • FIG. 4 shows the structure of the two-stage planetary gear from FIG. 1 in a detailed axial section.
  • the shaft 4 connected to the internal combustion engine carries a planet carrier 20 in the form of a plate-like flange, on the outer edge of which three pins 21 i (see also FIG. 5) are let in at an angular distance of 120 °, which are the axes of rotation of the planet wheels 2 i of the first gear stage define.
  • the disks 22 i of the planet gears 2 i have only a fraction of the axial dimension of the teeth and are also broken through in order to keep the moment of inertia of the wheels as low as possible.
  • the ring gear 3 i is screwed to a flange 23 which has a cylindrical projection 24 as an engagement surface for a braking device.
  • the planet carrier 20 has an arm 27 projecting over the axial width of the first gear stage, at the end of which a further pin 21 ii is anchored, each of which carries a planet gear 2 ii of the second gear stage.
  • a flange 25 fixedly connected to the ring gear 3 ii forms a carrier for plates 26 of a plate brake.
  • FIG. 5 shows a simplified cross section along the line VV from FIG. 4.
  • the gear wheels 1 i , 2 i , 3 i of the first stage are shown in section, the sun gear 1 ii is partially covered.
  • the arms 27 of the planet carrier 20, which hold the planet gears 2 ii of the second stage, extend through spaces which exist between the planet gears 2, the first stage.
  • the ring gear 3 ii of the second stage is identical in size to the ring gear 3 i of the first.
  • the suns are denoted by 1 i and 1 ii in FIG.
  • FIG. 2 shows the diagram of a second embodiment of a two-stage planetary gear for an electrical machine according to the invention.
  • the shafts 4 and 6 connected to the internal combustion engine and the electrical machine are each firmly connected to a sun gear 1 i and 1 ii .
  • Planet gears 2 i and 2 ii of the two stages are firmly coupled to one another by a common axis 7.
  • basically three different transmission ratios can be set, two of them by locking a ring gear each and the third by locking the planetary movement, that is to say holding the axes 7 of the pairs of planet gears.
  • a braking device used on the ends of the axes 7 exerts a force in the axial direction as by the arrows 9 indicated in Figure 2, and the axes like a planetary movement, but not the planet gears prevents rotation about the axes.
  • FIG. 2a A modification is shown in FIG. 2a.
  • a braking force F acts on a cylindrical outer surface 8, which surrounds the edge of the planet carrier 20 ', in the same way as on the ring gears of the configurations described with reference to FIGS. 1, 4 and 5 or 2.
  • braking devices of the same type can be used to brake the movement of the axles 7 as well as the rotation of the ring gear 3 ii , which simplifies the construction.
  • the shaft 4 of the internal combustion engine is firmly connected to a large sun gear 1 i which meshes with the planet gears 2 i .
  • These are rotatably mounted on a planet carrier 20 ′′ and mesh with planet gears 2 ii of the second stage, which are mounted on the same carrier 20 ′′.
  • the latter are in engagement with a small sun gear 1 ii , which is coupled via a shaft 6 to an electrical machine provided as a starter or generator of the motor vehicle.
  • the gearbox has two gear ratios. In the first, the ring gear 3 ii of the second stage is fixed, in the second it is the planet carrier 20 ′′. No ring gear is required in the first stage, which has a clear advantage in terms of compactness and moment of inertia, since this ring gear, if it were present, would have to be significantly larger and heavier than that of the second stage.
  • the planet carrier 20 ′′ holds the planetary gears 2 ii of the second stage with the aid of arms that are partially cranked outside the sectional plane of the figure in the direction of the planetary movement, which is indicated in the figure by a broken line.
  • the planet carrier 20 '' is like the planet carrier 20 'of Figure 2A by a cylindrical Lockable outer surface 8 engaging brake.
  • FIG. 6 shows in axial section a gear 33 with two multi-disc brakes 35 i , 35 ii and an actuating device for actuating the two multi-disc brakes together.
  • the structure of the transmission corresponds to that of Figure 1 and will not be described again in detail.
  • the disk brakes 35 i , 35 ii each comprise a disk set connected to a ring gear 3 i , 3 ii and a disk set connected to an axially displaceable carrier 40.
  • the displaceable plate set is pressed by a spring (not shown) against an adjusting ring 41, which FIG. 7 shows in a perspective view. Due to the force of the spring, the adjusting ring 41 is clamped axially between the lamellae and a set of stationary rollers 42.
  • the adjusting ring 41 bears two circumferentially extending ramps 43, on the surface of which a roller 42 runs when the adjusting ring 41 around the shaft 4 or 6 is rotated.
  • the disk carrier 40 are different shifted far axially, that means the brake is different strongly attracted.
  • the two adjusting rings 41 are connected via a bridge 44 a telescopic mechanism rotatably but axially against each other slidably connected.
  • One of Collars 41 carries one on its outer circumference Sprocket, which meshes with a pinion 45, which by a motor 46 via a reduction gear 47 is driven.
  • the ring gear extends over an angular segment whose size is at least that of each ramp corresponds to 43 spanned angle.
  • FIG 9 shows a perspective view of the Adjusting device from Figure 6 and the geared motor arrangement 46.47.
  • the ring gear has the shape of a on a collar 41 fixed segment 48, from which the bridge 44 to the second Collet 41 goes out.
  • the bridge 44 consists of two interlocking, axially rail-guided Elements.
  • the components 41 to 45 and 48 can be regarded as a single adjusting device which, by simply rotating the pinion 45, allows the braking devices 35 i , 35 ii to be brought into different positions when coupled.
  • FIG. 8 shows an example of a possible height profile of the ramps 43 of the two adjusting rings 41 from FIG. 6 along their circumference.
  • the lower curve corresponds to the collar shown in FIG. 7.
  • Corresponding positions of the adjusting ring 41 in FIGS. 7 and 8 are each identified by letters a to e.
  • the circles on the curves in positions a to e each symbolize the roller 42 assigned to the ramp in different positions of its path.
  • the ramp from FIG. 7 has a height h a (see lower curve in FIG. 8), in which the assigned braking device brakes but does not block completely.
  • Figure 10 shows schematically a variant of a Setting device.
  • the collars 41 both serrated on at least part of its outer circumference and comb with pinions 45 which, on a common Shaft 49 mounted, driven by motor 46 become.
  • the width of the pinion is respectively the teeth of the adjusting wheels 42 so dimensioned that the adjusting wheels due to the interaction the (not shown in this figure) Axially move ramps with the braking devices can, without doing with the pinions 45 except Intervention to come.
  • Shoe brake in the form of a shoe brake is shown in Figure 11.
  • This designated with the reference numeral 50 Shoe brake includes two arms 51 which are around in relation to the fixed transmission 33 (not shown here) Axes 52 are pivotable. Each arm 51 carries a brake shoe 53.
  • the arms 51 carry opposite ends at their ends, pointed triangular noses 54.
  • An adjusting lever 55 is about a stationary axis 58 pivotable and carries one on a first arm 57 Rider 59 with a recess into which the lugs 54 intervention.
  • the rider 59 is pivoted of the lever 55 perpendicular to the axis of the Gear can be moved in the direction of arrow A.
  • the second arm 56 of the actuating lever 55 acts as in FIG 12, together with a cam disk 60 and thus determines the height of the rider 59 on the noses 54.
  • To make the profile of the cam disc more recognizable to make is around their center of rotation dash-dotted circle, its radius is equal to the maximum radius of the cam disc. The further down the rider 59 in FIG.
  • FIG. 13 shows a side view of a transmission 33 with two shoe brakes 50 i , 50 ii with the construction described above, which are each assigned to the two stages 34 i , 35 ii of the transmission.
  • Two cam disks 60 i , 60 ii are connected to a servomotor 46 via a common shaft 49.
  • the two cam disks are identically shaped, but are arranged in mirror image to one another, so that in the position shown in FIG. 13 a second lever 56 i is lowered, the associated shoe brake 50 I is thus open and the other second lever arm 56 II is raised, the shoe brake 50 ii is closed accordingly.
  • each control lever is assigned its own cam disk 60 I , 60 II .
  • the two actuating levers engage on a common cam disk with an offset angle.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
EP99963199A 1998-11-14 1999-11-04 Elektrische maschine mit getriebe Expired - Lifetime EP1047874B1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19852607 1998-11-14
DE19852607 1998-11-14
DE19927521 1999-06-16
DE19927521A DE19927521C2 (de) 1998-11-14 1999-06-16 Elektrische Maschine
PCT/DE1999/003522 WO2000029744A1 (de) 1998-11-14 1999-11-04 Elektrische maschine mit getriebe

Publications (2)

Publication Number Publication Date
EP1047874A1 EP1047874A1 (de) 2000-11-02
EP1047874B1 true EP1047874B1 (de) 2004-07-28

Family

ID=26050156

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99963199A Expired - Lifetime EP1047874B1 (de) 1998-11-14 1999-11-04 Elektrische maschine mit getriebe

Country Status (5)

Country Link
US (1) US6409622B1 (enExample)
EP (1) EP1047874B1 (enExample)
JP (1) JP4582607B2 (enExample)
BR (1) BR9906923A (enExample)
WO (1) WO2000029744A1 (enExample)

Families Citing this family (42)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE513350C2 (sv) * 1998-12-23 2000-08-28 Unic Ab Transmission vid personbilar
JP3917390B2 (ja) * 2001-07-06 2007-05-23 株式会社日立製作所 発電電動装置
JP2004060520A (ja) * 2002-07-29 2004-02-26 Denso Corp スタータ
EP1455085A3 (en) * 2003-03-04 2009-12-16 HONDA MOTOR CO., Ltd. Automotive internal combustion engine control system
JP4165362B2 (ja) * 2003-10-08 2008-10-15 株式会社デンソー スタータ
US7185496B2 (en) * 2004-07-12 2007-03-06 Honeywell International, Inc. Synchronizing stationary clutch of compression braking with a two spool gas turbine engine
JP4789000B2 (ja) * 2006-02-16 2011-10-05 Ｓｍｃ株式会社 減速比自動切換装置
AT505119A1 (de) * 2007-04-23 2008-11-15 Blum Gmbh Julius Antrieb für ein bewegbares möbelteil
JP4784567B2 (ja) * 2007-07-05 2011-10-05 株式会社デンソー スタータ
JP4831043B2 (ja) * 2007-10-11 2011-12-07 株式会社デンソー スタータ
JP4957530B2 (ja) * 2007-12-05 2012-06-20 株式会社デンソー スタータ
FR2931774B1 (fr) * 2008-05-30 2010-06-04 Peugeot Citroen Automobiles Sa Procede de controle d'un couple alternateur-variateur d'un ensemble moteur de vehicule automobile.
NL2005511C2 (en) 2010-05-17 2011-11-21 Dti Group Bv Transmissie voor een elektrische of hybride aandrijving,
US8808132B2 (en) * 2012-05-31 2014-08-19 Gm Global Technology Operations, Llc Differential with integrated torque vectoring
CN103644265A (zh) * 2013-12-09 2014-03-19 中联重科股份有限公司 工程机械及其行星减速机构
CN104003048B (zh) * 2014-05-20 2016-08-24 无锡瑞巴斯医疗器械有限公司 一种移动药箱
US10591025B2 (en) 2016-02-29 2020-03-17 Deere & Company Integrated starter-generator device with power transmission
US10487918B2 (en) 2016-02-29 2019-11-26 Deere & Company Integrated starter-generator device with power transmission
US10479187B2 (en) 2017-11-29 2019-11-19 Deere & Company Integrated hybrid power system for work vehicle
US10519920B2 (en) * 2018-01-17 2019-12-31 Deere & Company Automatic two-mode high reduction power transmission system
US20190376484A1 (en) * 2018-06-06 2019-12-12 GM Global Technology Operations LLC Vehicle Engine Electric Starter Motor with Multiple Speed Ratios
US11060496B2 (en) 2019-04-16 2021-07-13 Deere & Company Multi-mode integrated starter-generator device
US10933731B2 (en) 2019-04-16 2021-03-02 Deere & Company Multi-mode integrated starter-generator device with magnetic cam assembly
US10821820B1 (en) 2019-04-16 2020-11-03 Deere & Company Multi-mode starter-generator device transmission with single valve control
US10948054B2 (en) 2019-04-16 2021-03-16 Deere & Company Multi-mode integrated starter-generator device with solenoid cam actuation apparatus
US11156270B2 (en) 2019-04-16 2021-10-26 Deere & Company Multi-mode integrated starter-generator device with transmission assembly mounting arrangement
US10975937B2 (en) 2019-04-16 2021-04-13 Deere & Company Multi-mode integrated starter-generator device with cam arrangement
US10920733B2 (en) * 2019-04-16 2021-02-16 Deere & Company Multi-mode integrated starter-generator device with preloaded clutch
US10975938B2 (en) 2019-04-16 2021-04-13 Deere & Company Multi-mode integrated starter-generator device with electromagnetic actuation assembly
US10968985B2 (en) 2019-04-16 2021-04-06 Deere & Company Bi-directional integrated starter-generator device
US10920730B2 (en) 2019-04-16 2021-02-16 Deere & Company Multi-mode integrated starter-generator device with dog clutch arrangement
US10900454B1 (en) 2020-04-03 2021-01-26 Deere & Company Integrated starter-generator device with unidirectional clutch actuation utilizing a biased lever assembly
US11193560B1 (en) 2020-05-29 2021-12-07 Deere & Company Work vehicle multi-speed drive assembly with bifurcated clutches
US11415199B2 (en) 2020-05-29 2022-08-16 Deere & Company Bi-directional multi-speed drive
US12043981B2 (en) 2020-09-25 2024-07-23 Deere & Company Work vehicle drive with multiple electric machines and torque combining assembly
US11326570B1 (en) 2020-10-26 2022-05-10 Deere & Company Multi-mode integrated starter-generator device with unidirectional input
US11624170B2 (en) 2021-02-25 2023-04-11 Deere & Company Work vehicle multi-speed drive assembly with clutch retention mechanism
US11866910B2 (en) 2021-02-25 2024-01-09 Deere & Company Work vehicle multi-speed drive assembly with output control clutch
US11719209B2 (en) 2021-03-29 2023-08-08 Deere & Company Integrated starter-generator device with unidirectional clutch actuation utilizing biased lever assembly
US11761515B2 (en) 2021-05-20 2023-09-19 Deere & Company Work vehicle multi-speed drive assembly with guided dog clutch
US11686374B2 (en) 2021-07-23 2023-06-27 Deere & Company Work vehicle multi-speed drive assembly providing multiple gear ratios at same step ratio
EP4375539A1 (en) 2022-11-23 2024-05-29 Goodrich Actuation Systems SAS Gear device

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH193425A (de) * 1936-09-04 1937-10-15 Scintilla Ag Einrichtung an Brennkraftmaschinen mit einer als Anlassmotor und als Stromerzeuger dienenden elektrischen Maschine.
JPS5338376B2 (enExample) * 1973-06-28 1978-10-14
DE2504867A1 (de) * 1975-02-06 1976-08-19 Helmut Koerner Antriebsaggregat
US4077282A (en) * 1976-12-23 1978-03-07 Deere & Company Transmission
CA1209375A (en) * 1982-04-08 1986-08-12 John H. Kerr Incrementally variable transmission
JPS5963254U (ja) * 1982-10-20 1984-04-25 ヤンマー農機株式会社 遊星歯車式変速装置
DE3246230A1 (de) * 1982-12-14 1984-06-14 Volkswagenwerk Ag Getriebeanordnung
SU1103008A1 (ru) * 1983-01-19 1984-07-15 Всесоюзный заочный машиностроительный институт Привод стартер-генератора
US4708030A (en) * 1985-03-18 1987-11-24 Sundstrand Corporation Multi-range starter-generator drive
JPS63101545A (ja) * 1986-10-15 1988-05-06 Matsushita Electric Works Ltd 遊星変速装置
US4862770A (en) * 1987-07-13 1989-09-05 Borg-Warner Automotive, Inc. Two-speed alternator drive
FR2639413B1 (fr) * 1988-11-18 1993-10-15 Potain Boite de vitesses a deux rapports et a changement de vitesse a l'arret
FR2643520B1 (fr) 1989-02-21 1991-04-26 Valeo Alternateur-demarreur avec dispositif d'accouplement automatique
US4920815A (en) * 1989-04-24 1990-05-01 Eaton Corporation Single shaft shifting mechanism
US5418400A (en) * 1993-12-27 1995-05-23 Ford Motor Company Integrated generator and starter motor
US5482512A (en) * 1994-04-12 1996-01-09 General Motors Corporation Electro-mechanical hybrid powertrain with self-engaging brakes for starting the engine
JP3045650B2 (ja) 1994-11-04 2000-05-29 株式会社エクォス・リサーチ 車両用変速機
DE19748045A1 (de) * 1997-05-09 1998-11-12 Bosch Gmbh Robert Starter-Generator-Maschine mit variabler Getriebeübersetzung für eine Kraftfahrzeug-Brennkraftmaschine

Also Published As

Publication number Publication date
US6409622B1 (en) 2002-06-25
BR9906923A (pt) 2000-10-10
JP4582607B2 (ja) 2010-11-17
EP1047874A1 (de) 2000-11-02
JP2002530570A (ja) 2002-09-17
WO2000029744A1 (de) 2000-05-25

Similar Documents

Publication Publication Date Title
EP1047874B1 (de) Elektrische maschine mit getriebe
DE19927521C2 (de) Elektrische Maschine
WO1999018648A1 (de) Elektrische maschine
DE112015002682T5 (de) Elektrische bremsbetätigungsvorrichtung für fahrzeuge
EP1650071A2 (de) Antriebsanordnung
DE102004060991A1 (de) Steuerung eines Planetengetriebes mit einem Startergenerator im Nebenabtrieb durch Drehzahlsteuerung des Startergenerators
DE102017127146B3 (de) Schaltgetriebe und Elektroantrieb mit einem Schaltgetriebe
AT5363U1 (de) Verteilergetriebe mit steuerbarer reibungskupplung
DE102005048611A1 (de) Antriebsanordnung
DE102020200123A1 (de) Stirnraddifferential und Antriebssystem
EP1220987A1 (de) Vorrichtung zum kuppeln mindestens eines nebenaggregats mit einem hauptaggregat
DE19736549A1 (de) Extruder-Antriebsvorrichtung für Doppelschneckenextruder
EP1254326A1 (de) Differentialgetriebe mit sperrkupplung und mit einer solchen ausgestattetes verteilergetriebe für kraftfahrzeuge
DE2343804C2 (de) Zahnradgetriebe für ein zyklisch variables Übersetzungsverhältnis
EP2861445A1 (de) Übersetzungs- und ausgleichsgetriebe sowie motor- und getriebeeinheit
DE69916861T2 (de) Leistungsgetriebe mit mehreren planetenradantrieben
DE102021109712A1 (de) Schalteinheit und Antriebseinheit für einen elektrifizierten Antriebsstrang eines Kraftfahrzeugs sowie Achsmodul
DE102005034340B4 (de) Planetengetriebe und Stellantrieb für Armaturen mit einem Planetengetriebe
DE19959394C2 (de) Antriebsvorrichtung für eine Umformmaschine
DE3011133C2 (de) Vorrichtung zur Betätigung von Stromschaltern, insbesondere von Steuerstrom-Endschaltern
DE19810592A1 (de) Elektrische Maschine
DE29924088U1 (de) Antrieb für Verstellvorrichtungen in Kraftfahrzeugen
DE102019121215A1 (de) Planetengetriebe mit einem integrierten Freilauf
EP3810447B1 (de) Antriebseinheit, antriebsanordnung und hybrid-kraftfahrzeug
DE833890C (de) Reibungsgetriebe

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

17P Request for examination filed

Effective date: 20001127

17Q First examination report despatched

Effective date: 20030620

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR IT

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

REF Corresponds to:

Ref document number: 59910067

Country of ref document: DE

Date of ref document: 20040902

Kind code of ref document: P

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20050429

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20120124

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20121123

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20121217

Year of fee payment: 14

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59910067

Country of ref document: DE

Effective date: 20130601

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130601

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20140731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131202