• 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 a rotatable gear (4) is arranged, and with a spring element (9) 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 (14) on the main gear (2) and a second Stirnverzahnungsteil (15) on the rotatable gear (4) is formed. The rotatable toothed wheel (4) is guided over at least one, at least approximately annular guide web (16) formed in the area of the spur toothing.
    公开号:AT514070A4
    申请号:T50381/2013
    申请日:2013-06-11
    公开日:2014-10-15
    发明作者:
    申请人:Miba Sinter Austria Gmbh；
    IPC主号:
    专利说明:

    1
    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 part of the spur gear teeth on the main gear and a second part of the spur gear teeth is formed on the rotatable gear.
    Such a gear arrangement is known for example from the applicant's WO 2005/09030 A1, which is a gear for a backlash-free spur gear with a hub, with a hub-carried sprocket along a pitch axis normal pitch in two sub-rings, namely in a hub-fixed collar part and in a relation to this coaxially rotatably mounted ring collar, divided, and with a hub enclosing 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, in the circumferential direction of the Sprocket are arranged 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 and AT 510 283 B1.
    It has been shown in the operation of such gear arrangements, that under some circumstances this is subject to a relatively high wear. 2/22 N2013 / 08000 2
    The object of the invention is to improve an initially mentioned gear arrangement with respect to the operation.
    This object is achieved in the gear arrangement mentioned above in that the rotatable gear is guided over at least one annular guide web formed in the region of the spur gear teeth.
    The advantage here is that is relieved by this outer guide of the rotatable gear on the main gear during the relative movement to the main gear, the area on the hub on the main gear on which the rotatable gear is arranged, whereby the wear on this hub is reduced and thus the service life of the Gear arrangement can be extended. In addition, a larger guide surface is provided by the outer guide, whereby the wear in the gear arrangement can be further reduced. Due to the larger guide surface, it is additionally possible to improve the acoustic behavior of the gear arrangement by the leadership of the rotatable gear per se can be improved in the relative adjustment to the main gear. An optionally occurring "rattling" of the gear arrangement can thus be reduced or avoided.
    It should be noted at this point that an outer guide in the sense of the invention on the one hand understood that the guide surface on the rotatable gear is pointing away from the hub on the main gear, radially outwardly facing surface, as described in the description of the Figures will be explained. Regardless of or in addition to an external guide in the context of the invention is a guide with a guide surface, wherein the guide surface is formed close to the root circle of the spur toothing.
    The term "close to the root circle" is understood to mean that the distance between the guide surface and the root circle in the radial direction is at most 50% of the root diameter.
    According to a variant embodiment of the gear arrangement, it is provided that the at least one annular guide web is formed on the rotatable gear 3/22 N2013 / 08000 3. It can thus be simplified, the manufacture of the guide bar, in particular if the gear arrangement is at least partially made of sintered components. Namely, it is possible to form the guide bar in the axial direction above the toothing, whereby the moldability and the releasability of the sintered component can be simplified. In addition, the guide bar is better accessible by this design, for example, to calibrate this or subject the guide surface of a post. In addition, so that the overall length of the gear assembly in the axial direction may be lower, since the guide bar can be integrally formed dipping or engaging in the main gear in the axial direction.
    According to another embodiment, it can be provided that the at least one annular guide web engages in an annular groove. It can thus be achieved a further improvement of the leadership of the rotatable gear on the main gear by the radial mobility of the rotatable gear is limited in two directions. It can thus be achieved at the hub of the main gear a relatively large spacing of the rotatable gear from the surface of the hub, whereby in operation of the gear assembly on the hub substantially no more wear occurs. If the axial securing of the relative position of the rotatable toothed wheel with respect to the main toothed wheel does not take place in part via the hub, this design variant can optionally completely dispense with the design of the hub on the main toothed wheel.
    It is also possible that the rotatable gear is biased in the axial direction against the main gear. By this bias, so not only the axial securing of the relative position of the rotatable gear in relation to the main gear, the investment of the guide surface of the guide web can be improved on the corresponding mating guide surface. In addition, a reduction of the noise behavior of the gear arrangement can be achieved by damping the damped due to the friction between the main gear and the rotatable gear relative movement of the rotatable gear to the main gear. The "gear arrangement" system can thus be combined with less dynamics, i. carrier. Due to the axial bias, it is also possible to perform the guide bar in the radial direction with a smaller width and still achieve a secure guidance of the rotatable gear on the main gear.
    It can also be provided that the region between the hub on the main gear and the spur gear on the main gear and the rotatable gear is at least partially frusto-conical. Although this has the disadvantage that the gear arrangement compared to a non-frustoconical but straight design has more mass, we achieved with this design, that despite the axially projecting guide web, a reduction in the installation space size of the gear assembly in the axial direction is possible. The disadvantage of the larger mass but can be counteracted by the provision of recesses in the rotatable gear and / or in the main gear.
    A further improvement of the leadership of the rotatable gear on the main gear is achieved when a width of the annular guide web in the axial direction of the gear assembly corresponds to at least a width of the second part of the spur gear on the rotatable gear in the axial direction. It can thus be achieved a better distribution of force in the gear assembly.
    In order to reduce the friction on the guide surfaces sliding against each other during the relative displacement of the rotatable gear to the main gear on the main gear and the rotatable gear can be provided that a friction-reducing coating is arranged or formed on the annular guide web.
    According to a further embodiment of the gear arrangement can be provided that a guide surface against which abuts the annular guide web, in the axial direction has a greater width than the annular guide web. It is thus achieved that the axial end face of the guide web is not applied to the main gear and therefore no friction occurs during the relative displacement of the rotatable gear to the main gear in this area. 5/22 N2013 / 08000 5
    For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
    Each shows in a schematically simplified representation:
    1 shows a first embodiment of the gear arrangement in exploded view and in an oblique view.
    Figure 2 shows the gear assembly of Figure 1 in exploded view and oblique view from another perspective.
    Fig. 3 shows a detail of another embodiment of the gear arrangement cut in cross section.
    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, wherein 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 are to be transferred to the new situation mutatis mutandis when a change in position.
    1 and 2 show in exploded view a gear arrangement 1. This 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, a hub fifth has, which is in particular integrally formed 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 anti-twist protection against this shaft, so of course does not mean that the 6/22 N2013 / 08000 6
    Main gear 2 does not turn. Regarded relative to the rotatable gear 4, the main gear 2 but "fixed".
    For arrangement or recording on the shaft, the hub 5 may have a recess 6 in the form of a central bore. Alternatively or additionally, the hub 6 on both sides - viewed in the axial direction - be formed with an anti-rotation, for example, formed on the end faces in the axial direction splines. Other types of anti-rotation device, as known in the art, are also possible, e.g. by shrinking, by splines, etc.
    The rotatable gear 4 is biased in the circumferential direction 3 relative to the main gear 2 by means of a spring element 9, which is in this case so-called Ω - spring, as is known from the prior art. For the bias of a support bar 10 on the main gear 2 and a support bar 11 is formed on the rotatable gear 4. The spring element 7 abuts against these support webs 10, 11 with its two open end regions 12, 13. In the assembled state of the gear arrangement 1, the two support webs 10,11 abut each other, so that no gap is formed therebetween. But it is also possible that the two support webs 10, 11 are arranged spaced apart in the assembled state.
    The toothed wheel arrangement 1 has an end toothing on an outer circumference, a first end toothing part 14 extending over the circumference of the main toothed wheel 2 and a second end toothing part 15 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 teeth parts 14, 15.
    Unlike the gear arrangements known from the prior art, the rotatable gear 4 is not or not exclusively guided on the inside of the hub 2, but the rotatable gear 4 has an outer guide. To form this outer guide, the rotatable gear 4 is guided in the region of the peripheral toothing of the gear arrangement 1 via an annular guide web 16. 7/22 N2013 / 08000 7
    With regard to the definition of the wording "in the area of the spur toothing", reference is made to the above statements.
    In the embodiment of the gear arrangement 1 shown in FIGS. 1 and 2, the guide web 16 is formed on the rotatable gear 4, in particular made in one piece with this.
    It should be noted at this point that the main gear 2 and / or the rotatable gear 4 is preferably produced by a sintering process, ie, a sintered component (s) is / are.
    The guide web 16 is preferably annular. However, it is also an embodiment possible, is formed in the guide bar 16 is approximately annular, i. that the guide web 16 is formed by a plurality of circular ring sections, for example two, three or four, etc., which are arranged or formed in the circumferential direction along the circular ring one behind the other and in particular spaced from each other. In other words, the guide web 16 may have a plurality of segments arranged one behind the other.
    In addition to the extension of the guide web 16 in the circumferential direction 3, this has a width extension in the axial direction. When the guide bar 16 is formed on the rotatable gear 4, the guide bar 16 extends in the direction of the main gear 2 and immersed in this, so that the two Stirnverzahnungsteile 14, 15 of the face gear in the assembled state of the gear assembly 1 at least approximately abut each other.
    By "at least approximately" is meant that manufacturing due to the main gear 2 and / or the rotatable gear 4 in the region of the spur gearing a deduction 17 or 18 may be formed so that the two spur gear teeth 14, 15 are slightly spaced from each other when the rotatable gear 4 rests in the axial direction on a corresponding end face 20 in the axial direction of the main gear 2 via an end face 19.
    In order to enable the dipping of the guide bar 16 in the main gear 2, this has below the spur gear portion 14 a offset 21, which is at least as wide in the axial direction, as a width 22 of the guide bar 16 in the axial direction ,
    By this offset 21, a guide counter-surface 23 is formed, on which, viewed in the radial direction, outer guide surface 24 of the guide web 16 in the assembled state of the gear arrangement 1 is applied.
    Favor both the guide surface 24 and the guide counter-surface 23 are formed as cylindrical surfaces. However, there is also the possibility that the guide surface 24 and the guide counter-surface 23 are designed to taper conically in the axial direction, ie as frustoconical surfaces. In the event that the guide web 16 is formed by a plurality of segments, as stated above, these embodiments are adapted accordingly. After the guide counter-surface 23 is formed in the radial direction below the spur gear part 14 and the spur gear part 14 preferably extends over the entire circumference of the gear wheel arrangement 1, the guide counter-surface 23 preferably extends continuously in the circumferential direction 3.
    The thickness of the guide web 16 in the radial direction depends on the required mechanical strengths.
    According to a variant embodiment of the gear arrangement 1 it can be provided that the guide web 16 is not arranged on the rotatable gear 4, but on the main gear 2. In this case, the guide counter surface 23 is on the rotatable gear 4. Further, the guide web 16 extends in this case in viewed in the axial direction in the direction of the rotatable gear 4. The above statements on the embodiment of FIGS. 1 and 2 apply in this embodiment adapted accordingly.
    FIG. 3 shows a further embodiment of the gear arrangement 1, which may be independent of itself, wherein the same reference numerals or component designations are again used for the same parts as in the preceding FIGS. 1 and 2. In order to avoid unnecessary repetition, 9/22 N2013 / 08000 9 is referred to the detailed description in the preceding Figs. 1 and 2 or referenced.
    After this further embodiment of the gear arrangement 1, which is shown in Fig. 3 fragmentary in cross-section, there is the possibility that the guide bar 16 engages in an annular groove 25.
    The guide web 16 can in turn be arranged on the rotatable gear 4 as described above. The groove 25 is formed on the main gear 2 below the spur gear portion 14 by a further, in particular ring-shaped web 26 is formed or arranged below the Führungsge-genfläche 23 and spaced therefrom. Alternatively, the web 26 can also have a plurality of segments arranged in the circumferential direction 3 (FIG. 1) one behind the other and in particular at a distance from one another, as has been described above for the guide web 16.
    A height 27 of the groove 25 in the radial direction can be dimensioned such that the guide web 16 bears against both the guide surface 24 on the guide counter surface 23 and with a lower surface 28 on one of the guide counter surface 23 opposite wall surface 29 of the groove 25. However, there is also the possibility that this wall surface 29 of the groove 25 spaced from the surface 28 is formed, so the width 27 of the groove 25 is greater than the thickness of the guide web 16 in the same direction.
    Further, a width 30 of the web 26 in the axial direction be dimensioned so that an axially facing end face 31 of the web 26 with the end face 20 in the same direction, which is formed below the Stirnverzahnungsteils 14, is formed in alignment. However, the width 30 can also be dimensioned so that the end face 31 of the web 26 ends in the axial direction in front of the end face 20, so that a gap is formed between the rotatable gear 4 and the main gear 2 in the region of the web 26 differently than shown. It can thus reduce the friction between the main gear 2 and the rotatable gear 4. 10/22 N2013 / 08000 10
    If the guide web 16 as described rests on both sides in the groove 25, both an outer guide and an inner guide can be formed on the guide web 16.
    It should be noted in this context that in all embodiments, in addition to the outer guide still the inner guide of the rotatable gear 4 on the hub 5 is possible.
    Also in this embodiment of the gear arrangement 1 there is the possibility of reversed execution, i. the guide web 16 is formed on the main gearwheel 2 and the groove 25 on the rotatable gearwheel 4. In this case, the rotatable gear 4 may also have two webs which project in the direction of the main gear, between which the groove 25 is formed.
    It should be noted that it is generally possible, although not the preferred embodiment of the gear arrangement 1, that a plurality of guide webs 16, which are formed according to the above embodiments, on the main gear 2 and / or on the rotatable gear 4 may be formed. In this case, the plurality of guide ribs 16 are formed in the radial direction one above the other and spaced from each other in this direction.
    The following embodiments can be applied to all variants of the gear arrangement 1.
    To bias the further rotatable gear 4 also in an axial direction against the main gear 2, another spring element 32, e.g. in the form of a plate spring, be arranged, as shown in Figs. 1 and 2. The further spring element 32 can be arranged for example on the hub 5. Alternatively, the further spring element can also be arranged on the shaft, not shown, on which the gear arrangement 1 can be arranged.
    To secure the relative position of the rotatable gear 4 to the main gear 2 in the axial direction, a securing element 33, for example, a Seegering, be provided, as is also shown in Figs. 1 and 2. The securing element 33 can be arranged, for example, on the hub 5. 11/22 N2013 / 08000 11
    Alternatively, the further spring element can also be arranged on the shaft, not shown, on which the gear arrangement 1 can be arranged.
    It is also possible that a region 34 between the hub 5 on the main gear 2 and the spur gear part 14 on the main gear 2 is formed at least partially frusto-conical.
    Likewise, a region 35 between a bore 36 in the rotatable gear 4 for receiving the hub 5 of the main gear 2 and the spur gear 15 on the rotatable gear 4 is at least partially frusto-conical.
    The two frusto-conical regions 34, 35 are inclined in the same direction, so that the frusto-conical region 35 can be arranged on the rotatable toothed wheel 4 within the frusto-conical region 34 on the main toothed wheel 2.
    It can further be provided that the width 22 of the particular annular guide web 16 in the axial direction of the gear arrangement corresponds at least to a width 37 of the second spur gear part 15 on the rotatable gear 4 in the axial direction.
    Alternatively, however, the width 22 of the particular annular guide web 16 in the axial direction of the gear arrangement may be smaller than the width 37 of the second spur gear part 15 on the rotatable gear 4 in the axial direction.
    To reduce friction, it may be provided that a friction-reducing coating is arranged on the particular annular guide web 16. This coating can be provided on all adjoining and sliding surfaces, for example on the guide surface 24 (FIG. 1). Alternatively or additionally, this coating can also be provided on the corresponding surfaces of the main gear 2. 12/22 N2013 / 08000 12
    As a friction-reducing coating, for example, a lubricating varnish or a PTFE coating, etc., can be used.
    It can further be provided that a guide surface on which the particular annular guide web 16 rests, ie in particular the guide counter-surface 23 on the main gear 2, in the axial direction has a greater width than the particular annular guide web 16th
    In addition, it should be pointed out that the respective guide surfaces of the gear arrangement 1, ie in particular the guide surface 24 on the rotatable gear 4 and the guide counter surface 23 on the main gear 2, directly against each other, optionally interposition of the friction-reducing coating, so that so no in the region of the guide surfaces Gap is formed.
    In order to enable the engagement of the guide web 16 in the main gear 2, the support web 10 may be arranged on the main gear 2 spaced from the guide counter surface 23. Alternatively, the guide web 16 may be interrupted in the region of the support web 10, wherein the end faces of this recess are arranged in the guide web 16 spaced from the support web 10, so a width of the recess in the guide web 16 in the circumferential direction is greater, ie the width of the support web 10 in the circumferential direction to allow the rotatability of the rotatable gear 4 relative to the main gear. The guide bar 16 is therefore not a closed, complete circular ring in this case. When arranging the guide web 16 on the main gear the same applies accordingly in reverse.
    The embodiments show possible embodiments of the gear arrangement 1, wherein it should be noted at this point that various combinations of the individual variants are possible with each other.
    For the sake of order, it should finally be pointed out that, for a better understanding of the structure of the gear arrangement 1, these or their components 13 and 12 have been shown partially unevenly and / or enlarged and / or reduced in size. 14/22 N2013 / 08000
    LIST OF REFERENCE NUMBERS
    gearing
    main gear
    circumferentially
    gear
    hub
    recess
    spring element
    supporting web
    supporting web
    end
    end
    Spur gearing part
    Face gear part Guide web
    deposition
    deposition
    face
    face
    deposition
    Wide guide counter surface guide surface
    groove
    Bridge height
    area
    wall surface
    width
    face
    spring element
    fuse element
    Area
    Area
    drilling
    Width 15/22 N2013 / 08000RAT-AT-00
    权利要求:
    Claims (8)
    [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 (9), 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 (14) on the main gear (2) and a second Stirnverzahnungsteil (15) on the rotatable gear (4) is formed, characterized in that the rotatable gear (4) via at least one in the area the spur toothing trained, at least approximately annular guide web (16) is guided.
    [2]
    2. gear arrangement (1) according to claim 1, characterized in that the at least one at least approximately annular guide web (16) on the rotatable gear (4) is formed.
    [3]
    3. gear arrangement (1) according to claim 1 or 2, characterized in that the at least one at least approximately annular guide web (16) engages in an annular groove (25).
    [4]
    4. gear arrangement (1) according to one of claims 1 to 3, characterized in that the rotatable gear (4) is biased in the axial direction against the main gear (2).
    [5]
    5. gear arrangement (1) according to one of claims 1 to 4, characterized in that a region (34, 35) between the hub (5) on the main gear (2) and the spur gear teeth on the main gear (2) and the rotatable gear (4 ) is formed at least partially frusto-conical. 16/22 N2013 / 08000RAT-AT-00 2
    [6]
    6. gear arrangement (1) according to one of claims 1 to 5, characterized in that a width (22) of the annular guide web (16) in the axial direction of the gear arrangement (1) at least one width (37) of the second Stirnverzahnungsteils on the rotatable gear ( 4) corresponds in the axial direction.
    [7]
    7. gear arrangement (1) according to one of claims 1 to 6, characterized in that the at least approximately annular guide web (16) is arranged a friction-reducing coating.
    [8]
    8. gear arrangement (1) according to one of claims 1 to 7, characterized in that a guide mating surface (23) on which abuts the at least approximately annular guide web (16), in the axial direction has a greater width than the at least approximately annular guide web (23). 16). 17/22 N2013 / 08000RAT-AT-00
    类似技术:
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    同族专利:
    公开号 | 公开日
    CN104235310B|2019-10-01|
    US9410606B2|2016-08-09|
    CN104235310A|2014-12-24|
    AT514070B1|2014-10-15|
    US20140360300A1|2014-12-11|
    DE102014107924A1|2014-12-11|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US1558222A|1924-01-14|1925-10-20|Beetow Albert|Backlash take-up for gears|
    US20110030489A1|2009-08-05|2011-02-10|Gm Global Technology Operations, Inc.|Engine scissor gear assembly|AT521375A4|2018-11-15|2020-01-15|Miba Sinter Austria Gmbh|gearing|US1449903A|1923-03-27|Geab construction |
    US1619799A|1924-09-23|1927-03-01|Charles W Rounds|Nonchattering gear|
    JPH0141972Y2|1985-06-12|1989-12-11|
    JPS6263268A|1985-09-12|1987-03-19|Honda Motor Co Ltd|Gear drive device|
    US5194031A|1991-03-07|1993-03-16|Playskool, Inc.|Toy gear assembly|
    US5452622A|1993-02-09|1995-09-26|Magi, L.P.|Stress dissipation gear|
    JP3729189B2|2003-07-18|2005-12-21|ソニー株式会社|Imaging device|
    AT413748B|2004-03-22|2006-05-15|Miba Sinter Austria Gmbh|GEAR FOR A GAME-FREE HEAD WHEEL STAGE|
    DE102008050472B4|2008-10-04|2012-06-06|Thyssenkrupp Presta Teccenter Ag|Divided gear|
    KR101047607B1|2008-12-05|2011-07-07|현대자동차주식회사|Caesars Gear|
    AT507071B1|2008-12-29|2010-02-15|Miba Sinter Austria Gmbh|GEAR ARRANGEMENT|
    AT508701B1|2010-06-23|2011-05-15|Miba Sinter Austria Gmbh|GEAR ARRANGEMENT|
    AT510283B1|2010-09-29|2012-03-15|Miba Sinter Austria Gmbh|GEAR ARRANGEMENT|NL2012082C2|2014-01-14|2015-07-16|Vcst Ind Products Bvba|Scissor gear assembly.|
    DE102015206063B4|2015-04-02|2017-03-16|Schaeffler Technologies AG & Co. KG|Gear for a gear transmission|
    AT517424B1|2015-06-25|2019-09-15|Miba Sinter Austria Gmbh|Device for releasing play of meshing gears of a gear drive|
    NL2015189B1|2015-07-18|2017-02-07|Vcst Ind Products Bvba|Scissor gear assembly.|
    AT517484B1|2015-10-06|2017-02-15|Metaldyne Int Deutschland Gmbh|gearing|
    AT518787B1|2016-07-18|2018-01-15|Miba Sinter Austria Gmbh|gearing|
    AT520531B1|2018-04-24|2019-05-15|Miba Sinter Austria Gmbh|gear|
    CN108916357A|2018-07-17|2018-11-30|王小莉|A kind of antifatigue spur gear|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50381/2013A|AT514070B1|2013-06-11|2013-06-11|gearing|ATA50381/2013A| AT514070B1|2013-06-11|2013-06-11|gearing|
    US14/228,426| US9410606B2|2013-06-11|2014-03-28|Gear arrangement|
    CN201410131608.8A| CN104235310B|2013-06-11|2014-04-03|Geared system|
    DE201410107924| DE102014107924A1|2013-06-11|2014-06-05|gearing|
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