WO2013034123A1 - Schaltbares planetengetriebe für ein startergetriebe einer riemenscheibenanordnung eines kraftfahrzeugs - Google Patents
Schaltbares planetengetriebe für ein startergetriebe einer riemenscheibenanordnung eines kraftfahrzeugs Download PDFInfo
- Publication number
- WO2013034123A1 WO2013034123A1 PCT/DE2012/000826 DE2012000826W WO2013034123A1 WO 2013034123 A1 WO2013034123 A1 WO 2013034123A1 DE 2012000826 W DE2012000826 W DE 2012000826W WO 2013034123 A1 WO2013034123 A1 WO 2013034123A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- gear
- planetary
- planetary gear
- verspannrad
- ring gear
- Prior art date
Links
Classifications
-
- 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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/2863—Arrangements for adjusting or for taking-up backlash
Definitions
- the invention relates to a switchable planetary gear for a starter gear
- Pulley assembly of a motor vehicle with the aid of the translation between a crankshaft of an automotive engine and a connected via a pulley electric starter can be changed.
- a switchable planetary gear for a starter gear is a
- the planetary gear can be easily used in meshing engagement with the sun gear and the ring gear due to an existing example due to manufacturing tolerances backlash, resulting in a simple assembly.
- this backlash can be subsequently eliminated, so that due to rotational Gleichför- mieux the starting torque introduced by a drive motor caused gear rattle can be avoided and a pulley arrangement with low noise emissions is possible.
- Compared to a single planetary gear can be achieved by the planetary unit with the movable relative to the planetary Verspannrad a substantially backlash torque transmission between the sun gear and the ring gear. At least can be avoided in the circumferential direction between the sun gear and the planetary unit and / or between the planetary unit and the ring gear.
- an oil cushion is provided between the ring gear and the planetary unit, so that it may be sufficient to eliminate only the backlash between the planetary unit and the sun gear.
- the planetary gear and the Verspannrad lie in the circumferential direction on opposite sides of a tooth space of the sun gear and / or ring gear.
- the clamping wheel can be rotated in the circumferential direction relative to the planetary gear.
- the Verspannrad be rotated in the circumferential direction relative to the planetary gear and / or be displaced in the axial direction.
- the relative movement of the Verspannrads is limited to the planet, so that essentially only the backlash can be compensated.
- the Verspannrad can be locked non-positively and / or positively after compensation of the backlash in this bracing relative to the planet and / or be held by an applied force, in particular spring force in the bracing position.
- a bracing and / or a bracing which leads to an automatic compensation of backlash by a relative movement of the Verspannrads to the planet, wherein preferably the clamping force and / or the Verspannmoment from a defined minimum force and / or from a defined minimum torque can be overcome, for example, to allow assembly by hand.
- the pulley can cooperate with a traction means, via the KraftGermannebenaggregate, such as an oil pump, an air conditioning compressor of an air conditioner and / or a starter, in particular electric starter generator, can be connected.
- a torque can be transmitted via the pulley to the traction means for operating the motor vehicle auxiliary units via the switchable planetary gear, wherein the planetary gear in this drive mode in particular provides a 1: 1 translation.
- the planetary gear can be switched in such a way that a different ratio, for example a 3: 1 ratio, is set.
- the traction means may be designed as a rope, belt, in particular flat belt or V-belt, in particular poly-V belt, chain or the like.
- the traction means is in particular fiber-reinforced and / or has at least one metal wire, so that a particularly high tensile strength is given.
- the pulley may be contoured to drive the traction means radially outward to the traction means.
- the starter gear may have a brake disc connected to a component of the planetary gear, which may preferably be braked with a disc brake in order to vary the ratio of the planetary gear.
- the Verspannrad on a different number of teeth from the planet gear, wherein the Verspannrad meshes with either the sun gear or with the ring gear.
- the backlash can be compensated quickly and easily.
- the Verspannrad has a smaller number of teeth than the planet, so that the Verspannrad may have a smaller diameter than the planet and thereby easier to mesh only with the sun gear or the ring gear.
- the Verspannrad has a smaller by 1 number of teeth than the planet, so that sets a comparatively small relative movement of the Verspannrads to the planet or a relatively small torque difference between the Verspannrad and the planetary gear. Unnecessary braking torques or drag moments are thereby avoided.
- the Verspannrad is coupled indirectly or directly via a frictional force with the planetary gear force-transmitting. Due to the friction, the different rotational speed of the Verspannrads and the planetary gear can lead to a relative movement in the circumferential direction between the Verspannrad and the planet, so that the backlash between the planetary unit and the sun gear and / or the ring gear can be compensated automatically.
- between the Verspannrad and the planetary Rad provided a friction lining in order to provide the required frictional force of friction even at a correspondingly low normal force.
- the Verspannrad is biased by means of a Verspannelements, in particular compression spring or plate spring, relative to the planet gear.
- a sufficient force in particular spring force, can be provided to automatically compensate for backlash.
- the bracing element can, for example, engage both on the bracing wheel and on the planetary gear and in particular push away the bracing wheel far enough away from the planetary gear that the backlash can be compensated.
- a normal force between the Verspannrad and the planetary gear is applied via the bracing element, which leads to a sufficient frictional force between the Verspannrad and the planet gear to compensate for backlash.
- sudden torque changes can be damped by the bracing element, so that a damped torque transmission can be achieved.
- the clamping element exerts on the Verspannrad a substantially aligned in the axial direction of the planetary gear spring force. This makes it possible to guide the Verspannrad relative to the planet in the axial direction, for example via bolts, so that in particular the planetary unit can be easily mounted as a preassembled unit.
- the bracing element can in particular be designed as a spiral spring, preferably as a compression spring, or diaphragm spring, so that a simple structure can be achieved.
- the bracing member pushes the Verspannrad on the planet gear or away from the planet.
- the biasing member pushes the Verspannrad on the planetary gear
- a sufficient normal force between the Verspannrad and the planetary gear can be applied via the Verspannelement to rotate the Verspannrad relative to the planet by a circumferentially acting frictional force to compensate for backlash.
- the clamping element pushes the Verspannrad away from the planetary gear, the Verspannrad and the planetary gear can be pressed against opposing tooth flanks of a tooth space, in particular a helical sun gear and / or helical ring gear on the Verspannelement to compensate for backlash.
- the planetary gear and / or the Verspannrad at least one, in particular substantially aligned in the axial direction, receiving opening for mounting Acceptance of the Verspannelements, wherein in particular a plurality, preferably at least three, circumferentially substantially uniformly distributed receiving openings are provided.
- the bracing element can be provided in the installation space occupied by the bracing wheel and / or the planetary gear without significantly increasing the required installation space of the planetary unit.
- the bracing element can be configured as a spiral spring with a correspondingly large spring travel, since the bracing element can spring into the volume of the receiving opening.
- a sufficient clamping force can be applied to compensate for backlash and maintain even under load the balanced backlash.
- a plurality of receiving openings provided by a plurality of Verspannettin spring force can be made uniform in the circumferential direction, so that tilting of the Verspannrads and / or the planetary gear can be avoided.
- the planetary gear and / or the Verspannrad is helically toothed. Due to the helical gearing, a better coverage of the meshing teeth may result, resulting in lower noise emissions.
- the backlash between the planetary unit and the sun gear and / or the ring gear can be done by a simple axial displacement of the Verspannrads relative to the planetary gear.
- the Verspannrad and the planetary gear can be pressed against opposing tooth flanks of a tooth space in particular a helical sun gear and / or helical gear ring to compensate for backlash.
- a twisting of the Verspannrads relative to the planet gear is not required to compensate for backlash.
- the Verspannrad is connected to the planetary gear substantially rotationally fixed, in particular by means of at least one substantially axially extending securing bolt, wherein the Verspannrad is movable in the axial direction relative to the planetary gear substantially.
- the securing bolt twisting of the Verspannrads can be avoided relative to the planet. This allows a structurally simple to implement relative movement of the Verspannrads to the planet in the axial direction.
- the securing bolt can be received with clearance fit of a corresponding opening, in particular through hole.
- the invention further relates to a starter gear with a switchable planetary gear, which can be trained and developed as described above, wherein the planetary gear has a particular associated with the ring gear disc for varying the gear ratio of the planetary gear by braking the brake disc, in particular one preferably as a disc brake configured ring gear brake is provided for braking the ring gear of the planetary gear.
- the planetary unit of the planetary gear tooth play between the planet and the sun and / or ring gear can be subsequently eliminated, so that due to rotational nonuniformities of the torque introduced by a drive motor caused gear rattle can be avoided and a starter gear for a pulley arrangement for Drive of KraftGermannebenaggregaten with low noise emissions is possible.
- the gear ratio of the starter gear can be changed to start a connected to the starter gearbox of a motor vehicle via an electric starter in the starter gear initiated starting torque with a gear suitable for the start gear ratio to the To be able to transfer internal combustion engine.
- the braking of the brake disc can be terminated to provide a more suitable for the regular operation of the motor vehicle compared to the starting operation gear ratio.
- the invention further relates to a pulley arrangement for driving KraftGermannebenaggregaten, with a pulley for driving a connected to the KraftGermannebenaggregaten traction means, in particular via a freewheel connected to the pulley starter gear for transmitting a starter provided by a starting torque to a drive shaft, in particular crankshaft, an automotive engine wherein the starter gear has a switchable planetary gear for varying a gear ratio between the pulley and the drive shaft, in particular by means of a ring gear brake for braking the ring gear, wherein the switchable planetary gear as described above and can be further developed.
- the planetary unit of the planetary gear teeth between the planet and the sun and / or ring gear can be subsequently eliminated, so that due to rotational irregularities of the initiated by a drive motor starting torque gear rattle can be avoided and a pulley arrangement is made possible with low noise emissions.
- the drive shaft of the motor vehicle engine is optionally connected via a freewheel directly to the starter gear, in particular to the sun gear of the switchable planetary gear.
- FIG. 1 is a schematic sectional view of a built-switchable planetary gear in a first embodiment, a schematic schematic representation of the force ratios of a helical gear shift planetary gear, a schematic exploded view of a planetary unit for a switchable planetary gear in a second embodiment,
- FIG. 4 shows a schematic sectional view of a built-switchable planetary gear with the planetary unit of FIG. 3,
- FIG. 5 shows a schematic sectional view of the planetary unit of FIG. 3, a schematic exploded view of a planetary unit for a switchable planetary gear in a third embodiment
- Fig. 7 is a schematic sectional view of the planetary unit of Fig. 6 and
- FIG. 8 shows a schematic plan view of the planetary unit from FIG. 6.
- a drive shaft 12 of an internal combustion engine of a motor vehicle is connected via a freewheel 14 with a sun gear 16 of a motor vehicle.
- the sun gear 16 is supported for the freewheeling operation of the freewheel 14 via a bearing 22 on the drive shaft 12.
- the planetary gear 18 has a ring gear 24 to which a brake disk 26 may be connected in order to be able to change the transmission ratio of the switchable planetary gear 20 by braking the ring gear 24.
- the sun gear 16 and the ring gear 24 are coupled together via a planetary unit 28.
- the planetary unit 28 is mounted via a planetary bearing 30 with a bearing pin 32 of a planet carrier 34.
- the planetary unit 28 shown in Fig. 1 has a planetary gear 36 which meshes with both the sun gear 16 and the ring gear 24. Further, a first Verspannrad 38 and a second Verspannrad 40 is provided, wherein the first Verspannrad 38 meshes only with the sun gear 16 and not with the ring gear 24, while the second Verspannrad 40 meshes only with the ring gear 24 and not with the sun gear 16. In the illustrated embodiment, the first Verspannrad 38 and the second Verspannrad 40 substantially the same diameter as the planetary gear 36.
- the teeth of the sun gear 16 and the ring gear 24 are offset in the axial direction to each other such that the first Verspannrad 38 axially laterally to the toothing of the ring gear 24 and the second Verspannrad 40 axially laterally to the toothing of the sun gear 16 passes.
- the first Verspannrad 38 and the second Verspannrad 40 each have a number of teeth, which is one less than the number of teeth of the planetary gear.
- a first clamping element 42 designed as a plate spring the first clamping wheel 38 is pressed against the planetary gear 36 in such a way that a circumferential force between the first clamping wheel 38 and the planetary gear 36 results.
- the second Verspannrad 40 is pressed against the planetary gear 36 so with the aid of a designed as a plate spring second Verspannelements 44 that a circumferential direction acting frictional force between the second Verspannrad 40 and the planetary gear 36 results.
- Verspannen 42, 44 axial preload Verspanner 38, 40 is when rotating the at least one planetary gear 36 on the attacking friction and the different number of teeth between the bracing wheels 38, 40 and the planetary gear 36, a relative movement between the respective Verspannrad 38th , 40 and the planetary gear 36 caused by an existing backlash can be eliminated.
- the planet gear 36 may abut against a tooth flank of the sun gear 16 and the ring gear 24, while the associated Verspannrad 38, 40 may rest against the opposite tooth flank, whereby the backlash is balanced.
- the first clamping wheel 38, the second Verspannrad 40, the planetary gear 36 and the sun gear 16 and the ring gear 24 may each be configured straight teeth.
- first Verspannrad 38, the second Verspannrad 40, the planetary gear 36 and the sun gear 16 and the ring gear 24 are each helically toothed, the force relationships shown in Fig. 2 may result. Due to the axial force F ax applied by the clamping element 42, 44, the clamping wheel 38, 40 can be pushed away from the planetary gear 36 in the axial direction until the planetary gear 36 is pressed against a first toothed flange 46 of the sun gear 16 or the ring gear 36 and the clamping wheel 38 , 40 bears against one of the first tooth flank 46 opposite second tooth flank 48.
- the Verspannrad 38, 40 can be secured by means of axially extending locking pins 50 against relative rotation to the planetary gear 36.
- the bracing element 42, 44 is formed by a single spiral spring, which is guided radially inwardly from a hub 52 connected to the planetary gear 36 and at least partially in a formed in the planetary gear 36 annular receiving opening 54 can be accommodated.
- the pulley assembly 10 includes a pulley 56 that may be connected to the planetary carrier 34 or to the sun gear 16 of the shiftable planetary gear 18. With the help of the pulley 56 can be driven by a traction means ancillaries of the motor vehicle. In particular, can be connected via the traction means an electric starter, which can initiate a starting torque in the starter gear 20 via the pulley to start via the drive shaft 12, the motor vehicle engine.
- brake disc 26 can be braked by means of a disc brake to lock the ring gear 24 and adjust the translation of the planetary gear 18 for the start of the motor vehicle engine using the introduced via the drive shaft 12 in the motor vehicle engine torque.
- a single compression spring is provided by a plurality of clamping elements 42, 44 uniformly distributed over the circumference training replacing compression springs.
- the hub 52 of the planetary gear 36 on a safeguardsprofi- lation 58 which can be positively inserted into a corresponding inner profiling 60 of Verspannrads 38, 40 to prevent relative rotation of the Verspannrads 38, 40 relative to the planetary gear 36 even without separate locking pin 50 can.
- the hub 52 is connected to the Verspannrad 38, 40, so that in particular the circumferential profile 58 of the Verspannrad 38, 40 and the inner profiling 60 can be formed by the planetary gear 36.
- the receiving opening 54 may be formed by the Verspannrad 38, 40.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
- Gears, Cams (AREA)
- Transmission Devices (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201280043287.5A CN103782060B (zh) | 2011-09-09 | 2012-08-16 | 用于机动车的皮带盘组件的起动器传动装置的可换档行星齿轮传动装置 |
JP2014528851A JP2014527146A (ja) | 2011-09-09 | 2012-08-16 | 自動車のベルトプーリアッセンブリのスタータ伝動機構用の切換可能な遊星歯車式伝動機構 |
DE112012003745.6T DE112012003745A5 (de) | 2011-09-09 | 2012-08-16 | Schaltbares Planetengetriebe für ein Startergetriebe einer Riemenscheibenanordnung eines Kraftfahrzeugs |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011082387 | 2011-09-09 | ||
DE102011082387.5 | 2011-09-09 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2013034123A1 true WO2013034123A1 (de) | 2013-03-14 |
Family
ID=46934353
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2012/000826 WO2013034123A1 (de) | 2011-09-09 | 2012-08-16 | Schaltbares planetengetriebe für ein startergetriebe einer riemenscheibenanordnung eines kraftfahrzeugs |
Country Status (4)
Country | Link |
---|---|
JP (1) | JP2014527146A (de) |
CN (1) | CN103782060B (de) |
DE (2) | DE112012003745A5 (de) |
WO (1) | WO2013034123A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018219563A1 (de) * | 2017-05-31 | 2018-12-06 | Zf Friedrichshafen Ag | Montageeinheit für ein mehrstufiges planetengetriebe |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9512900B2 (en) * | 2015-05-08 | 2016-12-06 | E-Aam Driveline Systems Ab | Planetary gear mechanism with reduced gear lash |
CN110206868B (zh) * | 2019-06-29 | 2024-04-16 | 潍柴动力股份有限公司 | 一种齿轮组件及发动机 |
DE102019133860A1 (de) * | 2019-12-11 | 2021-01-14 | Schaeffler Technologies AG & Co. KG | Zahnradlageranordnung |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2544043A1 (fr) * | 1983-04-07 | 1984-10-12 | Henry Andre | Dispositif de rattrapage de jeu angulaire pour reducteurs a trains planetaires et reducteur le comprenant |
EP0296376A2 (de) * | 1987-06-26 | 1988-12-28 | Manfred Dipl.-Ing. Wittenstein | Spielfreies Planetengetriebe |
JPH04331849A (ja) * | 1991-05-02 | 1992-11-19 | Aiseru Kk | 遊星歯車式の減速機 |
RO106157B1 (ro) * | 1989-10-20 | 1993-02-26 | Mecanica De Masini Si Utilaj M | Reductor planetar cu joc de torsiune redus |
JPH0571593A (ja) * | 1991-03-19 | 1993-03-23 | Aiseru Kk | 遊星歯車式の減速機 |
US5240462A (en) * | 1991-03-19 | 1993-08-31 | Isel Co., Ltd. | Planetary reduction gear |
WO2001048397A2 (de) * | 1999-12-28 | 2001-07-05 | Diro Gmbh & Co. Kg | Verstellvorrichtung mit planetengetriebe |
DE10148961A1 (de) | 2000-10-12 | 2002-04-18 | Luk Lamellen & Kupplungsbau | Getriebe |
WO2003056141A1 (fr) * | 2001-12-26 | 2003-07-10 | Nittan Valve Co., Ltd. | Dispositif de reglage de distribution variable de type engrenage planetaire |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN1054910C (zh) * | 1995-11-17 | 2000-07-26 | 光阳工业股份有限公司 | 混合型摩托车自动变速装置 |
-
2012
- 2012-08-16 JP JP2014528851A patent/JP2014527146A/ja active Pending
- 2012-08-16 WO PCT/DE2012/000826 patent/WO2013034123A1/de active Application Filing
- 2012-08-16 CN CN201280043287.5A patent/CN103782060B/zh not_active Expired - Fee Related
- 2012-08-16 DE DE112012003745.6T patent/DE112012003745A5/de not_active Withdrawn
- 2012-08-16 DE DE201210214551 patent/DE102012214551A1/de not_active Withdrawn
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2544043A1 (fr) * | 1983-04-07 | 1984-10-12 | Henry Andre | Dispositif de rattrapage de jeu angulaire pour reducteurs a trains planetaires et reducteur le comprenant |
EP0296376A2 (de) * | 1987-06-26 | 1988-12-28 | Manfred Dipl.-Ing. Wittenstein | Spielfreies Planetengetriebe |
RO106157B1 (ro) * | 1989-10-20 | 1993-02-26 | Mecanica De Masini Si Utilaj M | Reductor planetar cu joc de torsiune redus |
JPH0571593A (ja) * | 1991-03-19 | 1993-03-23 | Aiseru Kk | 遊星歯車式の減速機 |
US5240462A (en) * | 1991-03-19 | 1993-08-31 | Isel Co., Ltd. | Planetary reduction gear |
JPH04331849A (ja) * | 1991-05-02 | 1992-11-19 | Aiseru Kk | 遊星歯車式の減速機 |
WO2001048397A2 (de) * | 1999-12-28 | 2001-07-05 | Diro Gmbh & Co. Kg | Verstellvorrichtung mit planetengetriebe |
DE10148961A1 (de) | 2000-10-12 | 2002-04-18 | Luk Lamellen & Kupplungsbau | Getriebe |
WO2003056141A1 (fr) * | 2001-12-26 | 2003-07-10 | Nittan Valve Co., Ltd. | Dispositif de reglage de distribution variable de type engrenage planetaire |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018219563A1 (de) * | 2017-05-31 | 2018-12-06 | Zf Friedrichshafen Ag | Montageeinheit für ein mehrstufiges planetengetriebe |
Also Published As
Publication number | Publication date |
---|---|
CN103782060A (zh) | 2014-05-07 |
DE102012214551A1 (de) | 2013-03-14 |
DE112012003745A5 (de) | 2014-05-22 |
JP2014527146A (ja) | 2014-10-09 |
CN103782060B (zh) | 2018-10-19 |
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