• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a gear arrangement (1) having a split spur gear, a main gear (2) and a gear wheel (4) rotatable relative thereto in the circumferential direction (3), the main gear wheel (2) having a hub (5) on which the rotatable gear (4) is arranged, and with a spring element (7), which is arranged between the main gear (2) and the rotatable gear (4), and with which the rotatable gear (4) in the circumferential direction (3) against the Main gear (2) is biased, wherein a first Stirnverzahnungsteil (10) of the spur gear teeth on the main gear (2) and a second Stirnverzahnungsteil (11) of the spur gear teeth on the rotatable gear (4) are formed, and the first Stirnverzahnungsteil (10) has a first axis of rotation ( 19) and the second spur gearing part (11) have a second axis of rotation (18). The second axis of rotation (18) of the second face gear part (11) is offset from the first axis of rotation (19) of the first face gear part (10).
    公开号:AT518787A4
    申请号:T50645/2016
    申请日:2016-07-18
    公开日:2018-01-15
    发明作者:
    申请人:Miba Sinter Austria Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a gear arrangement with a split spur gear, with a main gear and a relative to this relatively circumferentially rotatable gear, wherein the main gear has a hub on which the rotatable gear is arranged, and with a spring element between the main gear and the rotatable Gear is arranged, and with which the rotatable gear is biased in the circumferential direction against the main gear, wherein a first Stirnverzahnungsteil the face gear on the main gear and a second Stirnverzahnungsteil the face gear on the rotatable gear are formed, and the first Stirnverzahnungsteil a first axis of rotation and the second Stirnverzahnungsteil a have second axis of rotation.
    Such gear arrangements, which serve the play release of intermeshing gears, are already known from the prior art.
    For example, WO 2005/09030 A1 describes a gear for a backlash-free spur gear with a hub, carried by the hub sprocket, along an axis normal division plane in two sub-rings, namely in a hub-fixed rim part and in a coaxially rotatably mounted relative to this ring ring , Is divided, and with a hub enclosing the annular spring, which is formed with their mutually circumferentially opposite ends formed integrally with the two sub-rings, overlapping each other in the axial direction support webs, which are arranged in the circumferential direction of the ring gear one behind the other. The ring collar is secured axially on the hub, for example by means of a snap ring.
    Further such gear arrangements are known from AT 507 071 B1, AT 508 701 B1, AT 510 283 B1, AT 513 246 B1 and AT 514 070 B1.
    It has been shown in the operation of such gear arrangements that they may produce disturbing noises.
    The object of the invention is to improve an initially mentioned gear arrangement with regard to the acoustic behavior.
    This object is achieved in the gear arrangement mentioned above in that the second axis of rotation of the second Stirnverzahnungsteils is offset from the first axis of rotation of the first Stirnverzahnungsteils.
    The advantage here is that a balance of the guide clearance of the rotatable gear on the main gear in the region of the second Stirnverzahnungsteils is achieved by the coaxial offset of the axes of rotation of the two spur gear parts. Subsequently, it is achieved that both Stirnverzahnungsteile have improved engagement with the teeth of meshing with the gear assembly gear, since the conditional by the guide clearance displacement of the second Stirnverzahnungsteils can be compensated by the Koaxialversatz the axes of rotation. This more optimal engagement in turn leads to a reduction in noise during combing of the two gears. In addition, it has been observed that by the improved meshing of the two gears, a reduction of the wear on the toothing of the rotatable gear can be achieved. The optimized for the particular purpose tooth geometry of the toothing is so better effect.
    According to one embodiment of the gear arrangement can be provided that the maximum displacement of the second axis of rotation to the first axis of rotation is formed in an angular range between 60 ° and 120 ° to a arranged on the main gear first support bar for the spring element. It turned out namely in the operation of the gear arrangement that the effects described above can be further improved in such a trained gear arrangement.
    It may further be provided that the rotatable gear is guided inside and / or outside guided on the main gear. In other words, the guide circle diameter may be coaxial with the axis of rotation of the main gear. This design of the gear arrangement, this can be made easier, since the coaxial offset is limited exclusively to the axis of rotation of the second Stirnverzahnungsteils.
    For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
    Each shows in a simplified, schematic representation:
    Fig. 1 is a gear arrangement in exploded view;
    FIG. 2 shows the gear arrangement according to FIG. 1 in an exploded view and an oblique view; FIG.
    3 shows a cross section through the gear arrangement according to FIG. 1 in the assembled state;
    Fig. 4 shows a detail of the rotatable gear of the gear arrangement.
    By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component names, the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or component names. Also, the location information chosen in the description, such as top, bottom, side, etc. related to the immediately described and illustrated figure and to transmit mutatis mutandis to the new situation in a change in position.
    These gear arrangement 1, also called "split gear", has a main gear 2 and a relative to this relatively rotatable in a circumferential direction 3 gear 4, wherein the main gear 2 has a hub 5, which is in particular formed integrally with the main gear 2. The rotatable gear 4 is rotatably mounted on the hub 5 of the main gear 2.
    The main gear 2 may also be referred to as a fixed gear, which is connected against rotation with a shaft, not shown, is or will. The term "fixed" refers to the rotation against this shaft, so of course does not mean that the main gear 2 does not rotate. Regarded relative to the rotatable gear 4, the main gear 2 but "fixed".
    The rotation of the main gear 2 may be carried out according to the prior art, such as. by shrinking, by splines, etc ..
    For arrangement or recording on the shaft, the hub 5 may have a recess 6 in the form of a central bore.
    The rotatable gear 4 is biased in the circumferential direction 3 relative to the main gear 2 by means of a spring element 7, which is in this case so-called Ω - spring, as is known from the aforementioned prior art. For the bias of a support bar 8 on the main gear 2 and a support bar 9 is formed on the rotatable gear 4. The spring element 7 abuts against these support webs 8, 9 with its two open end regions. In the mounted state of the gear arrangement 1, the two support webs 8, 9 abut one another, so that no gap is formed between them. But it is also possible that the two support webs 8, 9 in the mounted state be-spaced apart from each other.
    The support web 8 is in particular formed integrally with the main gear 2 and protrudes in the direction of the rotatable gear 3 via the surface on which it is arranged before. The support web 9 is in particular formed integrally with the rotatable gear 3 and protrudes in the direction of the main gear 2 over the surface on which it is arranged before.
    The toothed wheel arrangement 1 has an end toothing on an outer circumference, a first end toothing part 10 extending over the circumference of the main toothed wheel 2 and a second end toothing part 11 extending over the circumference of the rotatable toothed wheel 4. The spur toothing is thus divided in the axial direction in the two spur gear parts 10,11.
    It should be noted that the face gear parts 10,11 exclusively refer to the teeth on the main gear 2 and the rotatable gear 4, and not on the below the respective Zahnfußkreises located areas of the main gear 2 and the rotatable gear 4th
    Furthermore, it should be noted that the rotatable gear 4 can not rotate by any angle relative to the main gear 2. Rather, the rotatability in the sense of this description is to be understood that the rotatable gear 4 can rotate relative to the main gear 2 by a certain maximum angle value, this maximum angle value results from the backlash that when combing the spur gear of the gear assembly with the Spur toothing of another gear results.
    To bias the further rotatable gear 4 also in the axial direction against the main gear 2, another spring element 12, e.g. in the form of a plate spring, be arranged. The further spring element 12 can be arranged for example on the hub 5 of the main gear 2 in the axial direction behind the rotatable gear 2, so that the rotatable gear 4 between the main gear 2 and the further spring element 12 is arranged.
    To secure the relative position of the rotatable gear 4 to the main gear 2 in the axial direction, a securing element 13, such as a lake low, may be provided. The securing element 13 can also be arranged on the hub 5 of the main gear 2. The securing element 13 may be arranged in the presence of the further spring element 12 at its rear side fitting, so that the further spring element 12 is arranged in the axial direction between the rotatable gear 2 and the securing element 13.
    The spring member 7 disposed in the axial direction between the main gear 2 and the rotatable gear 4 may be disposed in an annular groove 14 formed in the main gear 2.
    In the prior art documents mentioned above, the main gear and the rotatable gear are arranged completely coaxially with each other. By contrast, in the subject gear arrangement, the second spur gear part 11 has a coaxial offset relative to the first spur gear part 10. In other words, the two face gear parts 10, 11 have different axes of symmetry.
    It should be noted that the two face gear parts 10, 11 are made the same way, so both the same cross-sectional geometry (viewed in the axial direction) of the teeth and the same module have.
    In order to illustrate the coaxial offset, a section of the rotatable gear 4 is shown in FIG. 4. An inner circle 15 is defined by an inner diameter 16 (FIG. 1) of the rotatable gear 4. The inner diameter 16 is the diameter of the opening (bore) of the rotatable gear 4, which serves to receive the hub 5 of the main gear 2. An outer circle 17, however, is defined by the Zahnfußkreis the second Stirnverzahnungsteils 11, which is only indicated in Fig. 4. Dashed line, the displacement of the inner circle 17 is shown in Fig. 4.
    It should be noted that the representation of the displacement is exaggerated. In addition, in Fig. 4 further constructive details of the Zahnradkör pers of the rotatable gear 4 for better depictability of the shift is not shown.
    Due to the coaxial displacement of the gear body, so that part of the rotatable gear 4 below the Zahnfußkreises, a different axis of rotation than the second spur gear toothing part 11. The spur toothing part 11 has a second axis of rotation 18. After the rotatable gear 4 is arranged on the hub 5 of the main gear 2 (FIG. 3), the axis of rotation of the gear body is equal to a first axis of rotation 19 (FIG. 1) of the main gear 2. The second axis of rotation 18 of the second face gear 11 is offset from first rotation axis 19 of the first spur gear part 10.
    A distance 20 between the first rotation axis 19 and the second rotation axis 18 may be, for example, between 50 pm and 500 pm.
    The axial offset of the first to the second axis of rotation 18,19 of the two face gear parts 10,11 is taken into account in the manufacture of the rotatable gear 4. This is particularly simple when the rotatable gear 4 is produced by a sintering process, since then only the die must be shaped accordingly. In principle, however, a subsequent machining of the rotatable gear 4 is possible, in which case the rotatable gear 4 is made at the appropriate locations with an oversize.
    As part of the tests carried out, it has been found that the offset of the first to the second axis of rotation 18, 19 in a certain angular range - viewed in the circumferential direction 3 (FIG. 2) - is particularly advantageous. It can therefore be provided according to a variant of the gear arrangement 1, that the maximum displacement of the second axis of rotation 18 of the second Stirnverzahnungsteils 11 to the first axis of rotation 19 of the first Stirnverzahnungsteils 10 in an angular range between 60 ° and 120 ° to the arranged on the main gear first support bar 8 for the spring element 7 (Fig. 1) is formed. For example, the maximum offset may be at an angle of about 90 °, as shown in FIG. This maximum offset in the sem angular range of the distance between the two spur gear teeth 10, 11 is the largest.
    Although the second rotation axis 18 is eccentric to the first rotation axis 19, the two rotation axes of the gear main body (the gear main bodies are those parts of the main gear 2 and the rotatable gear 4, which are below the Zahnfußkreise the Stirnverzahnungsteile 10,11) formed coaxially with each other. In addition, the first axis of rotation 19 of the first face gear portion 10 is coaxially aligned therewith. It is thus possible that the rotatable gear 4 is guided inside on the hub 5 (Fig. 1).
    Alternatively, it can be provided that the rotatable gear 4 is formed externally guided. For this purpose, a guide web 21 may be formed on the rotatable gear 4, in particular in full circumference (FIG. 1). The guide bar 21 emerges in the assembled state of the gear assembly 1 in the annular groove 14 and in an annular groove of the main gear 2 a. Weitet, the guide bar 21 has a radially outer guide surface 22 which rests against a guide counter-surface 23 of the main gear 2 and is disposed immediately adjacent to this guide counter-surface 23. The guide counter-surface 23 is formed by the radially outer side wall of the annular groove 14 and an annular groove of the main gear 2.
    According to a further embodiment variant of the gear arrangement 1, it can be provided that the rotatable gear 4 is guided both internally and externally on the main gearwheel 2. The rotatable gear 2 can thus be guided both on the hub 5 of the main gear and on the guide web 21 (as stated above).
    The respective guide circle diameter are arranged in particular coaxially to each other.
    The exemplary embodiments show or describe possible embodiments of the gear arrangement 1, wherein it should be noted at this point that also different combinations of the individual design variants with one another are possible.
    For the sake of order, it should finally be pointed out that, for better understanding of the construction of the gear arrangement 1, it was not necessarily shown to scale.
    List of Reference Numerals 1 gear arrangement 2 main gear 3 circumferential direction 4 gear 5 hub 6 recess 7 spring element 8 supporting web 9 supporting web 10 spur gear part 11 spur gear part 12 spring element 13 securing element 14 annular groove 15 circle 16 inner diameter 17 circle 18 rotation axis 19 rotation axis 20 distance 21 guide web 22 guide surface 23 guide surface
    权利要求:
    Claims (3)
    [1]
    1. Gear arrangement (1) with a split spur gear, with a main gear (2) and relative to this relative in the circumferential direction (3) rotatable gear (4), wherein the main gear (2) has a hub (5) on which the rotatable Gear (4) is arranged, and with a spring element (7) which is arranged between the main gear (2) and the rotatable gear (4), and with which the rotatable gear (4) in the circumferential direction (3) against the main gear ( 2), wherein a first spur toothing part (10) of the spur gear teeth on the main gear (2) and a second spur gear part (11) of the spur gear teeth on the rotatable gear (4) are formed, and the first spur gear part (10) has a first rotation axis (19) and the second spur gearing part (11) has a second rotation axis (18), characterized in that the second rotation axis (18) of the second spur gearing part (11) is offset from the first rotation axis (19) of the first end vane (10) is.
    [2]
    2. gear arrangement (1) according to claim 1, characterized in that the maximum displacement of the second axis of rotation (18) to the first axis of rotation (19) in an angular range between 60 ° and 120 ° to a main gear (2) arranged first support web (8 ) is formed for the spring element (7).
    [3]
    3. gear arrangement (1) according to claim 1 or 2, characterized in that the rotatable gear (4) guided inside and / or externally guided on the main gear (2).
    类似技术:
    公开号 | 公开日 | 专利标题
    EP1728010B1|2010-11-24|Toothed wheel for a play-free spur gear set
    DE102014225192A1|2015-08-13|gear
    AT514070B1|2014-10-15|gearing
    EP3290751A1|2018-03-07|Planetary gear unit
    DE102017113900A1|2018-01-18|gearing
    WO2012037593A2|2012-03-29|Toothed wheel
    DE102009039993A1|2010-04-15|Transmission arrangement for crank-continuously variable transmission of motor vehicle, has drive shaft comprising independent and different individual parts, which are connected together in torque proof, centrical and axial manner
    DE102012222227A1|2014-06-05|Stirnraddifferentialgetriebe
    EP2683941B1|2015-05-13|Planetarytransmission for wind turbine
    EP2703693B1|2017-09-13|Planet carrier
    EP2161478B1|2011-10-19|Cogged wheel assembly
    DE102008046821B4|2016-06-09|Crankshaft for a variable compression internal combustion engine and variable compression internal combustion engine
    DE112013005300T5|2015-07-16|transmission device
    EP2646712B1|2016-03-23|Gear mechanism having helical toothing
    EP3230627A1|2017-10-18|Stepped planetary gear
    DE102016121393A1|2018-05-09|Ball bearing and method for its manufacture, fixed bearing, steering gear and steering system
    EP1831590B1|2009-03-25|Device, especially a planet gear, comprising an annular base body
    DE112018002557T5|2020-01-23|Compact differential wheel differential
    DE102017223019A1|2019-06-19|gearing arrangement
    DE102012207489A1|2013-11-07|Differential gear, in particular in the form of an axle differential
    DE102016006602A1|2016-12-01|Backlash-free planetary gear
    DE102012207493A1|2013-11-07|Differential gear for dividing driving power of propulsion system, spur gear pins that are received in addendum circle wall while gear pins are derived with engaging reaction force
    DE202006011877U1|2006-10-05|Reduction gear in particular for high speed electric drive, comprises planet carrier directly connected to eccentric shaft of second planetary unit
    DE102008063013B3|2010-08-12|Differential unit for use in axle drive of motor vehicle for torque distribution, has housing parts provided with flange sections that comprise multiple recesses, and ring wheel attached radially outside recesses at one of housing parts
    DE102013202089A1|2014-08-14|differential gear
    同族专利:
    公开号 | 公开日
    US20180017151A1|2018-01-18|
    US10145460B2|2018-12-04|
    AT518787B1|2018-01-15|
    DE102017113900A1|2018-01-18|
    CN107631003A|2018-01-26|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    WO2005090830A1|2004-03-22|2005-09-29|Miba Sinter Austria Gmbh|Toothed wheel for a play-free spur gear set|
    AT507071A4|2008-12-29|2010-02-15|Miba Sinter Austria Gmbh|Gear wheel arrangement for use in motor vehicle, has damping element arranged in axial direction between spring element and main gear wheel and/or rotating gear wheel, where spring element is arranged between wheels|
    DE102009015958A1|2009-03-27|2010-09-30|Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg|Component pairing for use in transmission of drive train of motor vehicle, has component in form of gear with component teeth and another component in form of gear with other component teeth|
    DE102009015947A1|2009-03-27|2010-10-07|Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg|Rattle-free mated part structure i.e. gear wheel mated part structure, for use in transmission i.e. stepped transmission, of drive train of motor vehicle i.e. passenger car, has anti-rattle part designed in elastically deformable manner|
    DE102009015953A1|2009-03-27|2010-10-07|Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg|Component pairing e.g. gear wheel pairing, for use in stepped transmission in drive train of passenger car, has anti-rattle component that is fixed to one of components by bayonet-type connection|
    DE102009015946A1|2009-03-27|2010-10-07|Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg|Mechanical component pairing i.e. gear wheel pairing, for use in stepped transmission of drive train of diesel engine of e.g. passenger car, has continuous radial spring element engaging in peripheral groove of anti-rattle component|
    AT508701A4|2010-06-23|2011-03-15|Miba Sinter Austria Gmbh|GEAR ARRANGEMENT|
    AT510283A4|2010-09-29|2012-03-15|Miba Sinter Austria Gmbh|GEAR ARRANGEMENT|
    DE102013110396A1|2012-10-25|2014-04-30|Miba Sinter Austria Gmbh|gearing|
    US20140360300A1|2013-06-11|2014-12-11|Miba Sinter Austria Gmbh|Gear arrangement|
    DE4424305C2|1994-07-09|2000-01-05|Zf Hurth Gotha Gmbh|Drive unit for an industrial truck consisting of electric motor and gearbox|
    US6997076B2|2003-02-10|2006-02-14|Delphi Technologies, Inc.|Gear backlash elimination and adjustable gear backlash mechanism|
    JP3729189B2|2003-07-18|2005-12-21|ソニー株式会社|Imaging device|
    DE202008010745U1|2007-12-27|2009-05-07|Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg|Rattle-free component pairing|
    EP2333381A4|2008-09-05|2013-08-21|Masahiro Ikemura|Gear device|
    DE102011122138A1|2011-12-22|2013-06-27|PMG Füssen GmbH|gearing|
    JP2014126048A|2012-12-25|2014-07-07|Keihin Corp|Gear and electric motor using gear|
    DE102012025210B4|2012-12-28|2014-08-14|Gkn Sinter Metals Holding Gmbh|Divided gear|
    AT514570B1|2014-02-13|2015-02-15|Miba Sinter Austria Gmbh|gear|CN109282015A|2017-07-20|2019-01-29|威强电工业电脑股份有限公司|It can avoid the protection structure of motor damage|
    DE102017126205A1|2017-11-09|2019-05-09|Man Truck & Bus Ag|Gear, in particular intermediate, for a gear drive|
    AT520531B1|2018-04-24|2019-05-15|Miba Sinter Austria Gmbh|gear|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50645/2016A|AT518787B1|2016-07-18|2016-07-18|gearing|ATA50645/2016A| AT518787B1|2016-07-18|2016-07-18|gearing|
    DE102017113900.1A| DE102017113900A1|2016-07-18|2017-06-23|gearing|
    US15/631,290| US10145460B2|2016-07-18|2017-06-23|Gear arrangement|
    CN201710504267.8A| CN107631003A|2016-07-18|2017-06-28|Gear arrangement component|
    [返回顶部]