EP2795160A1 - Getriebevorrichtung mit einem innenverzahnten hohlrad sowie zwei damit kämmenden stirnrädern - Google Patents

Getriebevorrichtung mit einem innenverzahnten hohlrad sowie zwei damit kämmenden stirnrädern

Info

Publication number
EP2795160A1
EP2795160A1 EP12794251.4A EP12794251A EP2795160A1 EP 2795160 A1 EP2795160 A1 EP 2795160A1 EP 12794251 A EP12794251 A EP 12794251A EP 2795160 A1 EP2795160 A1 EP 2795160A1
Authority
EP
European Patent Office
Prior art keywords
gear
transmission device
spur gears
ring gear
spur
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.)
Withdrawn
Application number
EP12794251.4A
Other languages
German (de)
English (en)
French (fr)
Inventor
Klaus-Peter Brenner
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.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
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
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP2795160A1 publication Critical patent/EP2795160A1/de
Withdrawn legal-status Critical Current

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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • F16H55/0806—Involute profile
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
    • 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
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
    • B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion
    • 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
    • B60K7/00—Disposition of motor in, or adjacent to, traction wheel
    • B60K7/0007—Disposition of motor in, or adjacent to, traction wheel the motor being electric
    • 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
    • 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
    • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
    • 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
    • B60K7/00—Disposition of motor in, or adjacent to, traction wheel
    • B60K2007/0038—Disposition of motor in, or adjacent to, traction wheel the motor moving together with the wheel axle
    • 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
    • B60K7/00—Disposition of motor in, or adjacent to, traction wheel
    • B60K2007/0061—Disposition of motor in, or adjacent to, traction wheel the motor axle being parallel to the wheel axle
    • 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
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H1/227—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts comprising two or more gearwheels in mesh with the same internally toothed wheel
    • 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
    • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
    • F16H2057/0012—Vibration-damping or noise reducing means specially adapted for gearings for reducing drive line oscillations

Definitions

  • the invention relates to a transmission device with an internally toothed ring gear and two meshing spur gears according to the closer defined in the preamble of claim 1.
  • Serial hybrid drives of city buses are formed, inter alia, with so-called electric portal axles whose drive wheels are operatively connected via gear devices with electric machines.
  • the serial hybrid drives allow a particularly economical and environmentally friendly operation in hard urban use with many start-up and braking operations.
  • the serial structure of a hybrid drive includes an internal combustion engine that is operated together with a generator as a power generator. There is no direct mechanical connection between the engine and the wheels. Via intermediate power electronics, the electric machines arranged in the region of the wheels can be supplied with power from the generator and / or an electrical energy store for driving the wheels and / or the electrical energy store can be recharged.
  • the power flow is in the serial hybrid drive but also reversible, the electric motors then act as generators during a regenerative braking operation of a city bus and feed the recovered power back into the electrical energy storage or batteries.
  • the internal combustion engine or diesel engine thus does not represent the sole source of energy and is therefore smaller in terms of its performance.
  • each arranged in the wheels of electric drives there is also the ability to provide a fully fledged driving performance when the engine is turned off, which, for example, emission-free and noise-reduced arrival and departure at stops is feasible.
  • emission-free and noise-reduced arrival and departure at stops is feasible.
  • consumption values in the area of the internal combustion engine can be reduced by up to 30%.
  • the serial principle shows its flexibility also in the design of city buses. Since the drive energy is supplied from the generator coupled to the internal combustion engine to the wheel-side electric drives via power cables, there are high degrees of freedom with regard to the arrangement of the drive components in the region of a bus. In addition, it is also possible to make a passenger compartment larger in comparison to conventionally designed city buses due to the smaller sized internal combustion engine.
  • the present invention is therefore an object of the invention to provide a transmission device with an internally toothed ring gear and two meshing spur gears available, which is characterized by a long service life and is operable with the lowest possible operating noise.
  • this object is achieved with a transmission device having the features of claim 1.
  • a transmission device having the features of claim 1.
  • a life compared to known from the prior art solutions is increased and Operating noise is reduced because the operating engagement angle between the spur gears and the ring gear is at least approximately equal.
  • the present invention is based on the finding that with at least approximately equal operating angles of engagement in the region of the toothings between the spur gears and the ring gear, deformations in the region of the ring gear causing the two-flank contact are avoided in a simple manner and the tooth forces in the area of meshing between the spur gears and the ring gear are at least approximately balanced.
  • a long service life and low operating noise are achieved in an advantageous development of the transmission device according to the invention characterized in that the operating engagement angle between the gears and the intermediate each at least approximately correspond to the operating engagement angles between the spur gears and the ring gear.
  • the ring gear is designed with a number of teeth corresponding to a straight natural number in order to achieve a favorable on the running behavior phase synchronism in the field of transmission device.
  • a profile overlap between the spur gears and the ring gear and between the spur gears and the intermediate gear in a further embodiment of the transmission device according to the invention in each case less than or equal to one.
  • a roughness depth in the region of the teeth of the spur gears, the ring gear and the intermediate gear is less than or equal to 2 ⁇ .
  • a low-noise operation causing another embodiment of the transmission device according to the invention is formed in the region between the spur gears and the ring gear and between the spur gears and the intermediate gear each with a jump coverage greater two.
  • the spur gear can be coupled in the region of the shaft to an output shaft of an electric machine of an electric portal axle of a vehicle and / or the ring gear can be brought into operative connection with a sun gear of a planetary gear device of an electric portal axle of a vehicle, whereby the vehicle executed with the transmission device , in particular a city bus, with high efficiency at the same time low operating noise is operable.
  • FIG. 1 is a highly schematic representation of a part of an electric axis with an embodiment of the transmission device according to the invention.
  • FIG. 2 shows the transmission device according to FIG. 1 in a single side view.
  • the electric portal axle 1 shows a highly schematized representation of a part of an electric axis 1 of a vehicle designed in the present case as a city bus with a compactly designed electric machine 3 which is offset relative to a vehicle axle 2 and designed as an asynchronous motor. Furthermore, the electric portal axle 1 comprises a transmission device 4, which is operatively connected to the electric machine 3 via a shaft 6 in the region of a first spur gear 5.
  • the transmission device 4 is coupled on the drive side via a ring gear 7 meshing with the first spur gear 5 to a transmission device 8, which is designed as a planetary gear.
  • the ring gear 7 is rotatably connected to a sun gear 9 of the transmission device 8.
  • the sun gear 9 meshes with planetary gears 10, which in turn with a ring gear 1 1 the transmission device 8 are engaged.
  • the transmission device 8 is coupled to a drive wheel 13, whereby the drive of the electric machine 3 is forwarded via the transmission device 4 and the transmission device 8 in the direction of the drive wheel 13.
  • the transmission device 4 has, in addition to the first spur gear 5 in the manner shown in more detail in Fig. 2, a further spur gear or a second spur gear 14, which also meshes with the ring gear 7 and is designed with a different number of teeth than the first spur gear 5 ,
  • the two spur gears 5 and 14 with a common intermediate 15 in engagement.
  • Both the second spur gear 14 and the intermediate gear 15 are each rotatably mounted on a housing fixedly executed shaft 1 6 and 17 respectively.
  • the designed as a power-split Hohlradportal transmission device 4 and running with four planet gears 10 gear device 8 are formed helically in the range of their gears.
  • An operating engagement angle in the region of the meshing between the first spur gear 5 and the ring gear 7 and the second spur gear 14 and the ring gear 7 are the same size.
  • the operating engagement angles between the first spur gear 5 and the intermediate gear 15 and between the intermediate gear 15 and the second spur gear 14 at least approximately correspond to the operational engagement angles between the first spur gear 5 and the ring gear 4 and the second spur gear 14 and the ring gear 7, respectively.
  • a sum of the backlash between the first spur gear 5 and the ring gear 7 and the sum of the flange keneutic between the first spur gear 5 and the intermediate gear 15, between the intermediate gear 15 and the second spur gear 14 and between the second spur gear 14 and the ring gear 7 at least approximately equal to zero.
  • the operating noise is due to the then same angle of rotation of the ring gear on the meshing between the first spur gear 5 and the intermediate gear 15, the intermediate gear 15 and the second spur gear 14 and the second spur gear 14 and the ring gear 7 and between the first spur gear 5 and the ring gear lower, since a radial deflection of the first spur gear 5 occurs when a load change occurs only to a small extent. This measure is independent of the execution of the teeth of the transmission device 4 and also the transmission device 8 as grade or helical gears.
  • the ring gear 7 is in the present case with an even number of teeth, preferably equal to -74, designed to achieve a phase synchrony of at least approximately 100%.
  • the jump coverage in the region of the teeth of the transmission device 4 is greater than two in order to reduce the operating noise to a minimum.
  • a profile overlap and a flank roughness in the region of the transmission device 4 are chosen as small as possible to reduce the tooth loss factors, while the normal engagement angle is set as large as possible.
  • a profile coverage depending on the particular application case is less than or equal to one and the roughness depth is less than or equal to 2 ⁇ , while the normal engagement angle greater than or equal to 25 ° is provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Power Engineering (AREA)
  • Gear Transmission (AREA)
  • Retarders (AREA)
  • Gears, Cams (AREA)
EP12794251.4A 2011-12-19 2012-11-21 Getriebevorrichtung mit einem innenverzahnten hohlrad sowie zwei damit kämmenden stirnrädern Withdrawn EP2795160A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011089021A DE102011089021A1 (de) 2011-12-19 2011-12-19 Getriebevorrichtung mit einem innenverzahnten Hohlrad sowie zwei damit kämmenden Stirnrädern
PCT/EP2012/073212 WO2013092085A1 (de) 2011-12-19 2012-11-21 Getriebevorrichtung mit einem innenverzahnten hohlrad sowie zwei damit kämmenden stirnrädern

Publications (1)

Publication Number Publication Date
EP2795160A1 true EP2795160A1 (de) 2014-10-29

Family

ID=47263294

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12794251.4A Withdrawn EP2795160A1 (de) 2011-12-19 2012-11-21 Getriebevorrichtung mit einem innenverzahnten hohlrad sowie zwei damit kämmenden stirnrädern

Country Status (7)

Country Link
US (1) US20140349801A1 (zh)
EP (1) EP2795160A1 (zh)
JP (1) JP2015505016A (zh)
KR (1) KR102078683B1 (zh)
CN (1) CN103958938B (zh)
DE (1) DE102011089021A1 (zh)
WO (1) WO2013092085A1 (zh)

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CN105864361A (zh) * 2016-06-03 2016-08-17 第拖拉机股份有限公司 一种拖拉机组合式后末端传动装置

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DE102013217522A1 (de) * 2013-09-03 2015-03-19 Schaeffler Technologies AG & Co. KG Planetenkoppelgetriebe
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DE102014213145A1 (de) 2014-07-07 2016-01-07 Schaeffler Technologies AG & Co. KG Planetengetriebe mit Betriebseingriffswinkelmodifikation sowie Hochgeschwindigkeitsantrieb mit dem Planetengetriebe
CN106706801B (zh) * 2017-02-15 2023-10-20 山东省分析测试中心 一种齿环旋转的液-液分配色谱仪
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CN110654220B (zh) * 2018-06-29 2022-03-18 比亚迪股份有限公司 轮边驱动系统以及车辆
CN110654224B (zh) * 2018-06-29 2022-03-18 比亚迪股份有限公司 轮边驱动系统以及车辆
CN110686049A (zh) * 2018-07-04 2020-01-14 比亚迪股份有限公司 车辆传动装置、车辆驱动系统和车辆
CN110686051B (zh) * 2018-07-04 2023-04-07 比亚迪股份有限公司 车辆传动装置、车辆驱动系统和车辆
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Also Published As

Publication number Publication date
CN103958938A (zh) 2014-07-30
WO2013092085A1 (de) 2013-06-27
DE102011089021A1 (de) 2013-06-20
CN103958938B (zh) 2017-08-11
US20140349801A1 (en) 2014-11-27
KR20140115319A (ko) 2014-09-30
KR102078683B1 (ko) 2020-02-19
JP2015505016A (ja) 2015-02-16

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