• 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 (12) comprising a fixed wheel (13) with a first face toothing (16) and a loose wheel (14) with a second face toothing (17), wherein the first face toothing (16) at least approximately at the same radial height the second spur gear (14) has a second axial end face (18) and the idler gear (14) has a second axial end face (19), and wherein the fixed gear (13) has at least at least one elastic connecting element (21) is connected to the loose wheel (14), to which end the elastic connecting element (21) on the one hand with the first axial end face (18) of the fixed wheel (13) and on the other hand with the second axial end face (19) of Losrades (14) is connected.
    公开号:AT517484A4
    申请号:T50852/2015
    申请日:2015-10-06
    公开日:2017-02-15
    发明作者:
    申请人:Metaldyne Int Deutschland Gmbh；Miba Sinter Austria Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a gear arrangement comprising a fixed gear with a first spur gear and a idler gear with a second spur gear, wherein the first end toothing is arranged at least approximately at the same radial height, as the second spur gear, wherein further the fixed gear a first axial end face and the idler gear have a second axial end face.
    Furthermore, the invention relates to a gear drive comprising a crankshaft with a first gear and a balance shaft with a second gear, wherein between the first gear and the second gear, an intermediate wheel is arranged, which is in meshing engagement with the first and the second gear.
    Balancing shafts are known in internal combustion engines used to reduce vibrations caused by free inertial forces and moments of inertia. The balance shaft is usually driven by the crankshaft, to which it is connected via a gear with this in operative connection. In order to reduce the noise of the intermeshing teeth between the balance shaft and the crankshaft and to absorb vibrations known from the prior art gears (also known as decoupled gears) known, the two parts via a rubber-elastic connecting element (also called rubber track or sleeve spring ) are connected. Reference may be made, for example, to the applicant's AT 514 590 B1 or the prior art cited therein.
    To produce the same direction of rotation of the crankshaft gear and the balance shaft gear, a so-called intermediate wheel is installed between these two, which is both in meshing engagement with the crankshaft gear and with the balance shaft gear. Since it is not necessary that the idler is also arranged on a separate shaft, a fixed axis can be used, on which the idler is rotatably mounted.
    To reduce the noise of the meshing gears, it is desirable if not only the gear on the balance shaft in the above sense is decoupled, but also the idler.
    Various variants of gear drives are also known from the prior art. Thus, e.g. WO 2013/189916 A1 a spur gear with at least two solid wheels mounted fixed to the housing, which are drivingly connected to each other via at least one pendulum mounted idler, the idler with at least one fixed gear in meshing engagement and by at least one preferably elastic tensioning element in a pressing against the fixed gear is pressed. It is thus achieved a vibration decoupling for damping the peaks of the drive torque in a three-directional drive.
    It is the object of the present invention to make the intermediate universal use in a gear drive. In particular, it is the object of the invention to improve the noise reduction in a gear drive with crankshaft and balance shaft.
    The object of the invention is achieved with the gear arrangement mentioned above, wherein the fixed wheel is connected via at least one elastic connecting element with the idler gear, for which the elastic connecting element is connected on the one hand with the first axial end face of the fixed wheel and on the other hand with the second axial end face of the idler gear.
    Next, the object of the invention with the aforementioned gear drive is achieved, in which the intermediate gear is designed as a gear arrangement according to one of the preceding claims with a fixed gear and a loose wheel.
    The advantage here is that it is possible with this configuration of the intermediate wheel that the elastic connecting element is either in the torque flow or not.
    In a formation of the intermediate wheel with decoupling via a sleeve spring, which is connected to radial end faces of the hub part and the sprocket part, and undivided sprocket, as is known from the prior art described above, the sprocket of the intermediate gear would be simultaneously with the teeth of the crankshaft and the balance wheel, against which it is made radially. The sprocket assumes an eccentric position, which is caused by the two simultaneously meshing with the intermediate gear wheels, especially when the balance shaft gear is decoupled. The restoring force is supplied by the sleeve spring. The torque is not transmitted through the elastic connecting element, but would be transferred from the crankshaft wheel to the intermediate gear and from there to the balance shaft gear purely through the gears, i. the elastic connecting element of the gear arrangement is not in the torque flow. It would be only the very low dynamic torque between the hub and ring gear of the idler and the small static torque due to bearing friction on the sleeve spring. The resulting shear and tensile stresses lead to a high mechanical stress on the sleeve spring.
    By dividing the teeth of the idler gear on the teeth of the idler gear and the toothing of the fixed wheel, it is possible that the teeth of the idler gear meshes exclusively with the teeth of the first gear of the crankshaft and is employed against them radially, and the teeth of the fixed gear exclusively with the teeth of the second gear of the balance shaft meshes. The torque is thus - in simplified terms - from the crankshaft in the idler gear, from there via the elastic connecting element in the fixed gear and from there into the balancer shaft. The gear on the
    Balance shaft is in particular also a decoupled gear. It is made easier with this embodiment of the intermediate gear an eccentric position of the Zwischenradteilverzahnung relative to the fixed axis or the bearing with which the intermediate gear is mounted on the fixed axis. Due to the small radial stiffness due to the elastic connecting element, it is possible to better make the gear arrangement against both meshing with him gears.
    In addition to this embodiment of the intermediate gear but there is also the possibility that the teeth of the fixed gear and the teeth of the idler gear mesh simultaneously with the teeth of the first gear of the crankshaft and the second gear of the balancer shaft. In this case, the teeth of the fixed wheel can be braced against the teeth of the idler gear, as will be explained in more detail below. Also in this case, a noise reduction can be achieved by reducing the backlash of the meshing gears.
    To further improve these effects, according to a preferred embodiment of the gear arrangement may be provided that the elastic connecting element is arranged exclusively between the first axial end face of the fixed gear and the second axial end face of the idler gear and exclusively connected to these axial end faces.
    It may further be provided that the first axial end face of the fixed wheel is formed in a recess of the fixed wheel and / or the second axial end face of the idler gear in a recess of the idler gear. It can thus be arranged at least partially within the fixed wheel and / or the idler gear, the elastic connecting element, whereby the axial length of the gear arrangement can be reduced.
    Preferably, this is the elastic connecting element at least partially made of a rubber-elastic material, wherein it is particularly preferred if this consists entirely of a rubber-elastic material. It can thus be better set the radial stiffness to a low value with a long service life of the elastic connecting element.
    Preferably, the elastic connecting element of the elastomeric material on the first axial end face of the fixed wheel and vulcanized onto the second axial end face of the idler gear, whereby a correspondingly good adhesion of the elastic connecting element to the end faces and thus in turn a longer service life can be achieved.
    According to another embodiment of the gear arrangement can be provided that the idler gear is biased in the circumferential direction against the fixed gear, whereby the gear assembly additionally the function of reducing the backlash when meshing engagement with the teeth of the other gears of the gear drive can be imparted. The game release is supported by the elastic connecting element.
    It can further be provided that the elastic connecting element has a widening cross section in the direction of the first axial end face of the fixed wheel and / or in the direction of the second axial end face of the loose wheel. It can thus be achieved with a low radial rigidity of the connecting element with high bonding strength at the end faces, in particular if the elastic connecting element consists at least partially of a vulcanized rubber.
    According to one embodiment of the gear drive can be provided, the fixed gear against the second gear of the balancer shaft and the idler gear are employed against the first gear of the crankshaft, whereby the employment of the gear arrangement can be improved to both gears.
    For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
    In each case, in a highly simplified, schematic representation:
    1 shows a gear drive in front view.
    2 shows a detail of a preferred embodiment of a gear arrangement in cross section;
    Fig. 3 shows a detail of another embodiment of the gear arrangement in front view.
    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 these position information in a change in position mutatis mutandis to transfer to the new location.
    In Fig. 1, a variant of a gear drive 1 is shown schematically. The gear drive 1 comprises a crankshaft 2 on which a first gear 3 is arranged rotationally fixed. The first gear 3 has a first toothing 4. This is arranged on a radially outer circumference of the first gear 3.
    It should be noted that all gears of the gear drive 1 are preferably designed as spur gears, which is formed or arranged on the outer circumference of the respective gear. For the sake of simplicity, these are shown in FIG. 1 as circular rings.
    The gear drive 1 further comprises at least one balance shaft 5, on which a second gear 6 is arranged rotationally fixed. The second gear 6 has a second toothing 7. This is arranged on a radially outer circumference of the second gear 6.
    In the illustrated embodiment of the gear drive 1, two balance shafts 4, each with a second gear 5 are arranged. But it can also be provided with the second gear 5, only one balance shaft 4.
    Between the first gear 3 and the second gear 6, an intermediate 8 is arranged. The toothing of the intermediate gear 8 is in meshing engagement with the first toothing 4 of the first gear 3 of the crankshaft 2 and the second gear 7 of the second gear 6 of the balance shaft 5. Unlike the first gear 3 and the second gear 6, the intermediate 8 is not arranged on a shaft but on an axis 9 via a bearing 10, for example, a rolling bearing stored. The axis 9 is rotatably connected to, for example, an engine block 11.
    The intermediate gear 8 is formed by a gear arrangement 12, which can be better seen in Fig. 2, which shows a section of a preferred embodiment of the gear assembly 12 in cross section.
    The gear arrangement 12 comprises a fixed wheel 13 (or first part gear) and a loose wheel 14 (or second part gear). The fixed gear 2 is mounted on the axle 9 via the bearing 10. Preferably, the fixed wheel 2 has a radially outwardly adjoining the bearing 10 hub part 15 on which the idler gear 14 is rotatably mounted.
    The fixed gear 13 has at its radially outer periphery a first spur gear 16. Also, the idler gear 14 has at its outer periphery a second spur gearing 17. The first spur gear 16 of the fixed gear 13 and the second spur gear 17 of the idler gear 14 are preferably at least approximately, in particular, arranged or formed at the same radial height, as can be seen from Fig. 2. The intermediate 8 of the gear drive 1 is thus formed by a split gear.
    The fixed wheel 13 has a first axial end face 18. The idler gear 14 has a second axial end face 19. In the assembled state of the gear arrangement 12, the first axial end face 18 of the fixed wheel 13 and the second axial end face 19 of the idler gear 14 are arranged adjacent to one another.
    Preferably, the first axial end face 18 of the fixed wheel 13 in a, in particular annular, recess 20, in particular groove-shaped recess 20, of the fixed wheel 13 is formed. But it is also possible that, alternatively or additionally, the second axial end face 19 of the idler gear 14 in a recess of the idler gear 14 (not shown in Fig. 2) is formed.
    Of course, there is also the possibility of forming the fixed wheel 13 and / or the idler gear 14 without such recesses 20, as shown in Fig. 2 for the idler gear 14.
    Between the first axial end face 18 of the fixed wheel 13 and the second axial end face 19 of the idler gear 14, at least one elastic connecting element 21 is arranged. About this elastic connecting element 21, the fixed gear 13 is connected to the idler gear 14. The elastic connecting element 21 is connected on the one hand with the first axial end face 18 of the fixed wheel 13 and on the other hand with the second axial end face of the idler gear 14.
    In principle, the elastic connecting element 21 may be any element which has sufficient elastic properties, such as at least one spring, in particular a spiral spring, in which case preferably a plurality of such elastic connecting elements 21 are arranged, in particular evenly distributed over the circumference of the gear arrangement ,
    In the preferred embodiment, however, the elastic connecting element 21 is at least partially formed from at least one rubber-elastic material, in particular at least one rubber. For example, the elastic connecting element 21 may at least partially consist of (X) NBR ((carboxylated) acrylonitrile-butadiene rubber), HNBR (hydrogenated nitrile rubber), a silicone rubber (VMQ), NR (natural rubber), EPDM (ethylene rubber). Propylene-diene rubber), CR (chloroprene rubber), SBR (styrene-butadiene rubber), etc., although mixtures of materials can be used therefrom. For example, the elastic connecting element 21 may consist of at least two connecting element parts made of different and in particular interconnected elastic materials.
    By "at least partially" is meant that in the elastic connecting element 21 e.g. Fasteners or stiffening elements, such as e.g. Fibers and / or threads, for example of metal, plastic, natural fibers, etc., or rods, etc. may be incorporated. Preferably, however, the elastic connecting element 21 consists exclusively of a rubber-elastic material.
    The connection of the elastic connecting element 21 with the first axial end face 18 of the fixed wheel 12 and the second axial end face 19 of the loose wheel 14, for example, by gluing or by mechanical connections, including in or on the elastic connecting element 21 and at least one (metallic) fasteners arranged can be done. Preferably, the connection of the elastic connecting element 21 with the first axial end face 18 of the fixed wheel 12 and the second axial end face 19 of the idler gear 14 but by direct vulcanization of the elastic connecting element 21, if this consists of at least one elastomeric material or is made from its precursor ,
    To improve the adhesion of the at least one elastic connecting element 21, at least one groove-shaped recess 22 may be formed in the first axial end face 18 of the fixed wheel 13 and / or in the second axial end face 19 of the idler gear 14, as shown in broken lines in FIG. 2. This groove-shaped recess 22 can be formed only in discrete areas, that is not fully or as a circular ring. Preferably, this at least one groove-shaped recess 22 has an undercut. For example, let a dovetail-shaped cross-section, viewed in the direction perpendicular to the axial direction of the gear arrangement 12.
    As already mentioned, at least one elastic connecting element 21 is arranged. Preferably, this is annular or disc-shaped, so that it can also be called a disc spring - in contrast to the above-mentioned sleeve spring. But it is also possible that a plurality of elastic connecting elements 21 are provided which extend over only a portion of the circumference of the gear arrangement 12. In this case, the plurality of elastic connecting elements 21 are arranged equidistantly distributed over the circumference of the gear arrangement 12.
    It is possible that the at least one elastic connecting element 21 is arranged extending into a radial end face in the gear arrangement 12. In the preferred embodiment of the gear arrangement 12, however, the at least one elastic connecting element 21 is arranged exclusively between the first axial end face 18 of the fixed wheel 13 and the second axial end face 19 of the loose wheel 14 and exclusively connected to these axial end faces 18, 19, as shown in FIG 2 is shown.
    FIG. 3 shows a section from a further embodiment of the gear arrangement 12, which may be independent of itself, wherein the same reference numerals as in FIG. 2 or component designations are again used for the description of FIG. 2 for the same parts. To avoid unnecessary repetition, reference is made to the detailed description of FIG.
    In this embodiment of the gear assembly 12, the idler gear 14 is biased in the circumferential direction of the gear assembly 12 against the fixed gear 13.
    It is thus achieved that the first end toothing 16 of the fixed wheel 13 is offset or rotated in the circumferential direction of the gear arrangement 12 to the second end toothing of the idler gear 14 by a specific or predeterminable angular amount. As a result, a so-called split gear is achieved, with which a play-free engagement in a further toothing of another gear, so for example, the first gear 3 and / or the second gear 6 of the gear drive 1 (Fig. 1), is possible. This can be done by twisting the idler gear 14 prior to installation or vulcanization of the at least one elastic connecting element 21 in the circumferential direction of the gear assembly relative to the fixed gear 13 and is fixed in this position with a pin or the like, after installation of the gear assembly 12 in one or the gear drive 1 is removed again.
    According to a further embodiment variant of the gear arrangement 12, it may be provided that the elastic connecting element 21 has a widening cross section in the direction of the first axial end face 18 of the fixed wheel 13 and / or in the direction of the second axial end face 19 of the loose wheel 14, as shown in FIG 2 is shown. A center region 23 of the elastic connecting element can thus have the smallest cross-section, viewed in the direction perpendicular to the axial direction of the gear arrangement 12.
    It is advantageous if the region adjoining directly to the first axial end face 18 of the fixed wheel 13 and / or the region of the elastic connecting element 21 directly adjoining the second axial end face 19 of the loose wheel 14 is or are provided with a rounding 24 whereby the mechanical strength of the elastic connecting element 21 can be improved. In particular, this rounding with a convex curvature, based on the elastic connecting element 21, be formed, as shown in Fig. 2.
    The teeth of the gears of the gear drive 1 and thus also the gear assembly 12 may generally be designed as a toothed face or Ge-radschrägverzahnung. The gear drive 1 may also be referred to as a spur gear.
    Further, the teeth of the fixed wheel 13 and the teeth of the idler gear 14 may have the same or a mutually different axial width.
    As already stated above, the toothing of the intermediate gear 8, that is the gear arrangement 12, against the first gear 3, i. its first gear 4 and / or against the second gear 6, i. According to a variant of the gear drive 1 can be provided that the fixed gear 13 against the second gear 6 of the balancer shaft 5 and the idler gear 14 against the first gear 4 of the crankshaft. 2 of the gear drive 1 are employed.
    The embodiments show possible embodiments, it being noted at this point that combinations of the individual embodiments are also possible with each other.
    For the sake of order, it should finally be pointed out that for a better understanding of the construction of the gear drive 1 or the gear arrangement 12, these have been shown to be partially uneven and / or enlarged and / or reduced in size.
    REFERENCE SIGNS 1 gear wheel 2 crankshaft 3 gear 4 toothing 5 balance shaft 6 gear 7 toothing 8 idler 9 axle 10 bearing 11 engine block 12 gear arrangement 13 fixed gear 14 idler gear 15 hub portion 16 spur gear 17 spur gear 18 end face 19 end face 20 recess 21 connecting element 22 recess 23 center portion 24 rounding
    权利要求:
    Claims (9)
    [1]
    claims
    1. Gear arrangement (12) comprising a fixed gear (13) with a first spur gear toothing (16) and a loose wheel (14) with a second spur gear toothing (17), wherein the first spur gear toothing (16) is arranged at least approximately at the same radial height as the second end toothing (17), wherein furthermore the fixed wheel (13) has a first axial end face (18) and the loose wheel (14) has a second axial end face (19), characterized in that the fixed wheel (13) is connected via at least one elastic connecting element (13). 21) is connected to the loose wheel (14), for which purpose the elastic connecting element (21) on the one hand with the first axial end face (18) of the fixed wheel (13) and on the other hand with the second axial end face (19) of the idler gear (14) is connected.
    [2]
    2. gear arrangement (12) according to claim 1, characterized in that the elastic connecting element (21) exclusively between the first axial end face (18) of the fixed wheel (13) and the second axial end face (19) of the idler gear (14) and exclusively with these axial end faces (18, 19) is connected.
    [3]
    3. gear arrangement (12) according to claim 1 or 2, characterized in that the first axial end face (18) of the fixed wheel (13) in a recess (20) of the fixed wheel (13) and / or the second axial end face (19) of the Losrades (14) is formed in a recess of the idler gear (14).
    [4]
    4. gear arrangement (12) according to one of claims 1 to 3, characterized in that the elastic connecting element (21) consists at least partially of a rubber-elastic material.
    [5]
    5. gear arrangement (12) according to claim 4, that the elastic connecting element (21) made of the rubber-elastic material on the first axial end face (18) of the fixed wheel (13) and on the second axial end face (19) of the idler gear (14) vulcanized.
    [6]
    6. gear arrangement (12) according to one of claims 1 to 5, characterized in that the idler gear (14) in the circumferential direction against the fixed gear (13) is biased.
    [7]
    7. gear arrangement (12) according to one of claims 1 to 6, characterized in that the elastic connecting element (21) in the direction of the first axial end face (18) of the fixed wheel (13) and / or towards the second axial end face ( 19) of the loose wheel (14) has a widening cross-section.
    [8]
    8. gear drive (1) comprising a crankshaft (2) with a first gear (3) and a balance shaft (5) with a second gear (6), wherein between the first gear (3) and the second gear (6) an intermediate (8) which is in meshing engagement with the first and the second gear (3, 6), characterized in that the intermediate wheel (8) as gear arrangement (12) according to one of the preceding claims with a fixed wheel (13) and a loose wheel (14) is formed.
    [9]
    9. gear drive (1) according to claim 8, characterized in that the fixed gear (13) exclusively against the second gear (6) of the balancer shaft (5) and the idler gear (14) exclusively against the first gear (3) of the crankshaft (2 ) are employed.
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    同族专利:
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    AT521377A4|2018-11-28|2020-01-15|Metaldyne Int Deutschland Gmbh|gear drive|US2061684A|1930-05-22|1936-11-24|Jr John L Spence|Backlash and wear take-up for gears|
    GB560469A|1942-10-01|1944-04-05|Aspin Frank Metcalfe|Improvements in or relating to gear wheels|
    US2845809A|1955-02-17|1958-08-05|Univ California|Pre-loaded gear|
    US3174356A|1963-07-11|1965-03-23|Gen Precision Inc|Variable spring-loaded antibacklash gear drive|
    FR2567229B1|1984-07-05|1990-02-02|James Damas|METHOD AND DEVICE FOR THE AUTOMATIC RETRACTION OF GAMES IN GEAR SYSTEMS|
    US4700582A|1985-05-31|1987-10-20|Ford Motor Company|Anti-backlash gear mechanism|
    JPS6436755U|1987-08-31|1989-03-06|
    JP2550626B2|1987-12-18|1996-11-06|トヨタ自動車株式会社|Gear tooth surface phasing method|
    DE3803700A1|1988-02-08|1989-08-17|Pierburg Gmbh|Gear wheel|
    JPH04300438A|1991-03-28|1992-10-23|Ricoh Co Ltd|Gear rotation transmission mechanism|
    JPH08177977A|1994-12-21|1996-07-12|Bridgestone Corp|Manufacture of torsional damper|
    JP3292052B2|1996-08-19|2002-06-17|三菱自動車工業株式会社|Gear structure|
    US5813335A|1996-12-18|1998-09-29|Heidelberg Harris Inc.|Apparatus for preventing backlash between the meshing teeth of a first and a second gear in a printing unit of a lithographic rotary printing press|
    US6354395B1|1997-08-04|2002-03-12|Delphi Technologies, Inc.|Delashed worm gear assembly and electric power assist apparatus|
    DE19750286A1|1997-11-13|1999-05-20|Bayerische Motoren Werke Ag|Drive arrangement for a second-order compensation device for a reciprocating piston internal combustion engine|
    DE19928960A1|1999-06-24|2000-12-28|Volkswagen Ag|Gear drive, e.g. for crankshaft of internal combustion engine; has extension ring to move third gear axially, so balancing tooth flange play of second gear engaging with first gear for heat expansion|
    US20020121152A1|2001-03-05|2002-09-05|White David C.|Phased gear set comprised of a pair of phased gears|
    DE10226850B3|2002-06-15|2004-01-22|Motorenfabrik Hatz Gmbh & Co Kg|Gear drive with automatic compensation of a backlash|
    AT413749B|2004-03-22|2006-05-15|Miba Sinter Austria Gmbh|GEAR FOR A GAME-FREE HEAD WHEEL STAGE|
    WO2008142131A2|2007-05-21|2008-11-27|Vcst Industrial Products|Split gear for avoiding backlash when engaging a mating gear|
    DE202008010745U1|2007-12-27|2009-05-07|Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg|Rattle-free component pairing|
    KR101036747B1|2008-08-28|2011-05-24|브레크니 크리스|Gear for the backlash removal|
    DE102008050472B4|2008-10-04|2012-06-06|Thyssenkrupp Presta Teccenter Ag|Divided gear|
    KR101047607B1|2008-12-05|2011-07-07|현대자동차주식회사|Caesars Gear|
    DE102009001403B3|2009-03-09|2010-08-05|Metallumform Gmbh|A scissors gear with an auxiliary gear elastically supported on a torque transmitting main gear|
    US8245591B2|2009-08-05|2012-08-21|GM Global Technology Operations LLC|Engine scissor gear assembly|
    DE102010029097B8|2010-05-19|2012-08-30|Metallumform Gmbh|Scheren gear with an opposite to a torque transmitting main gear elastically supported auxiliary gear|
    AT508701B1|2010-06-23|2011-05-15|Miba Sinter Austria Gmbh|GEAR ARRANGEMENT|
    CN201925442U|2010-12-14|2011-08-10|中国航空动力机械研究所|Planetary gear transmission mechanism and fixed gear ring thereof|
    AT511812B1|2011-12-02|2013-03-15|Miba Sinter Austria Gmbh|GEAR FOR A GAME-FREE HEAD WHEEL STAGE|
    TWI452218B|2012-02-07|2014-09-11|Nat Univ Chung Cheng|No backlash gear structure|
    US9010209B2|2012-03-05|2015-04-21|Caterpillar Inc.|Scissors gear assembly|
    AT512916B1|2012-06-19|2013-12-15|Avl List Gmbh|Spur gears|
    JP6017970B2|2013-01-09|2016-11-02|日立オートモティブシステムズ株式会社|Balancer device for internal combustion engine|
    AT513613B1|2013-02-08|2014-06-15|Miba Sinter Austria Gmbh|gearing|
    JP6568336B2|2013-06-06|2019-08-28|株式会社オティックス|Backlash adjustment method|
    CN203335784U|2013-06-09|2013-12-11|诸暨市振兴机器制造有限公司|Gear transmission system capable of eliminating gear transmission clearance|
    AT514070B1|2013-06-11|2014-10-15|Miba Sinter Austria Gmbh|gearing|
    WO2015027115A1|2013-08-21|2015-02-26|Pinnacle Engines, Inc.|Scissor gear with hydraulic backlash removal and hydraulic torsional damping|
    AT514590B1|2014-02-13|2015-02-15|Metaldyne Internat Deutschland Gmbh|gear|
    DE102014208268B3|2014-04-30|2015-05-13|Magna Powertrain Ag & Co. Kg|Gear for a play-free gear stage and hereby equipped gear stage|
    DE102014208269B3|2014-04-30|2015-09-03|Magna Powertrain Ag & Co. Kg|Method for producing a backlash-free gear stage|
    US9772030B2|2014-08-04|2017-09-26|Achates Power, Inc.|Split gear assembly with one-way roller clutch for controlling backlash in opposed-piston engines|
    US20160138697A1|2014-11-19|2016-05-19|Caterpillar Inc.|Gear assembly|US9732837B2|2015-02-09|2017-08-15|Hyundai Motor Company|Idle gear assembly|
    DE102017219547A1|2017-11-03|2019-05-09|Zf Friedrichshafen Ag|gearing|
    AT520531B1|2018-04-24|2019-05-15|Miba Sinter Austria Gmbh|gear|
    DE102018009330A1|2018-11-28|2020-05-28|Metaldyne International Deutschland Gmbh|Gear drive|
    KR20200077187A|2018-12-20|2020-06-30|현대자동차주식회사|Anti-backlash structrue of scissors gear|
    AT522433B1|2019-09-27|2020-11-15|Miba Sinter Austria Gmbh|gear|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50852/2015A|AT517484B1|2015-10-06|2015-10-06|gearing|ATA50852/2015A| AT517484B1|2015-10-06|2015-10-06|gearing|
    US15/271,617| US9927018B2|2015-10-06|2016-09-21|Gear assembly|
    DE102016118245.1A| DE102016118245B4|2015-10-06|2016-09-27|Gear drive|
    CN201610862308.6A| CN106560634B|2015-10-06|2016-09-29|Geared system|
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