• 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 main gear wheel (2) and a toothed wheel (4) rotatable relative thereto in the circumferential direction (3). 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) is biased against the main gear (2) wherein the main gear (2) at least a first support element (22) and the rotatable gear (4) at least a second support element (23), and wherein the spring element (7) between the first and the second support element (22, 23) and spaced therefrom to the first Surface (19) of the main gear (2) and the second surface (21) of the rotatable gear (4) is arranged.
    公开号:AT513613A4
    申请号:T50098/2013
    申请日:2013-02-08
    公开日:2014-06-15
    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 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 wherein the main gear has a first surface and the rotatable gear has a second surface, and with a spring member disposed between the first surface of the main gear and the second surface of the rotatable gear and with which the rotatable gear is biased in the circumferential direction against the main gear.
    Such a gear arrangement is known for example from WO 2005/090830 A1, which is a gear for a backlash-free spur gear with a hub, with a supported by the hub sprocket along an axis normal division plane in two sub-rings, namely in a hub-fixed ring part and in a this opposite coaxially rotatably mounted ring collar is divided, and with a hub surrounding the annular spring, which is supported with their mutually circumferentially opposite ends integrally formed with the two sub-rims supporting webs, which are arranged in the circumferential direction of the ring gear one behind the other.
    In such gear arrangements, it may happen during operation that the annular spring slips over the support webs and thus becomes trapped between the partial gears. As a result, this leads to the failure of the gear assembly and possibly to their damage. 1/19 N2013 / 02900 2
    The object of the present invention is to improve a gear assembly mentioned above in terms of reliability during operation.
    This object is achieved in the gear arrangement mentioned above in that the first gear on the first surface a plurality of this first surface in the direction of the second surface of the rotatable gear projecting first support elements and the rotatable gear more about this second surface in the direction of the first surface the main gear projecting second support elements, wherein the spring element between the first and the second support elements and thus spaced from the first surface of the main gear and the second surface of the rotatable gear is arranged.
    It is thus achieved that the spring element in the axial direction of the gear arrangement can be better kept in a flat position, whereby a distortion of the spring element is better avoided under a load. As a result, so that the sliding over of the spring element on the support webs on which the spring element normally supported, and the pinching of the spring element between the main gear and the rotatable gear better be prevented, whereby the reliability is improved.
    According to an embodiment variant, it can be provided that at least three second support elements are arranged. Although it is advantageous in view of the alignment of the spring element between the main gear and the rotatable gear, when the support surface is formed larger for the spring element, this embodiment has the advantage that thus the friction between the support elements and the spring element is reduced, thereby As a result, the wear on the support elements can be reduced.
    On the other hand, it can be provided according to a further embodiment, that at least four first support elements are arranged. This embodiment variant has the advantage that the location of the support elements on the first surface better adapts to the concrete load cases of the spring element bar, so in particular an asymmetrical arrangement of the support elements on the first surface of the main gear is possible ,
    To further reduce the wear due to friction between the support elements and the spring element, it is advantageous if the one or more first and / or second support element (s) are elongated with a longitudinal extent in a radial direction of the gear arrangement. Due to the elongated training in the radial direction thus a better support of the spring element is achieved on the support elements.
    It has proved to be advantageous if a ratio of a length to a width of the first and / or the second support element (s) is selected from a range of 2: 1 to 8: 1.
    The spring element can, as is known per se, be designed as an Ω spring. It is advantageous if in each case a first support element is arranged in the area adjacent to the open area of the Ω-spring, whereby a further improvement in terms of preventing the jamming of the spring element by slipping over the support webs of the main gear and the rotatable gear reaches can be.
    The first surface of the main gear and the second surface of the rotatable gear are spaced apart a distance x formed in the gear assembly. It is advantageous if a first height of the at least one first support element over the first surface, a second height of the at least one second support element on the second surface and a wall thickness of the spring element in the axial direction of the gear arrangement in total between 50% and 100% Distance x corresponds. By this embodiment, a further improvement in terms of the prevention of jamming of the spring element by slipping over the support webs of the main gear and the rotatable gear is also achieved. 3/19 N2013 / 02900 4
    In order to reduce wear due to friction, provision can be made for the support elements and / or the spring element to be or are provided with a sliding coating at least in regions. However, it is thus achieved in particular that the mobility of the spring element is improved in the circumferential direction of the gear assembly, whereby the rotation of the spring element can be better prevented under load By thus the spring element can be better kept in a flat position, in turn, the risk of jamming of the Spring element can be reduced.
    On the other hand, it is possible to deliberately increase the friction by the rotatable gear is biased with another spring element in the axial direction against the main gear. It is thus achieved a better acoustic behavior of the gear arrangement.
    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:
    Fig. 1 is a gear arrangement according to the prior art in an exploded view;
    Fig. 2 is a main gear of a gear arrangement in side view;
    3 shows a rotatable gear of a gear arrangement in side view;
    4 shows a section through a gear arrangement.
    5 shows a detailed view of the gear arrangement according to FIG. 4 corresponding to the circle designated by V in FIG. 4.
    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 positional items selected in 4/19 N2013 / 02900 5 of the specification, such as e.g. 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.
    Fig. 1 shows an exploded view of a gear arrangement 1, as it is known from the prior art. 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 has a hub 5, 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 hub 5 has a recess 6 in the form of a bore for receiving a shaft, not shown.
    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 formed in this case as a so-called Ω - spring, as described in WO 2005/090830 AI, which is thus in this scope of basic structure of the gear assembly 1 to the content of this description belongs. For the bias, as described above, the main gear 2, a support bar 8 is formed, which forms an assembly stop for another support bar 9 (see FIG. 3), which is augebildet on the rotatable gear 2. The spring element 7 rests against these support webs 8, 9 with its two open end regions 10, 11. The spring element 7 is arranged in a recess 12 in the main gear 2, ie between the main gear 2 and the rotatable gear 4th
    In order to secure the rotatable gear 4 in an axial direction 13, a locking ring may be arranged, as will be described below.
    On the other hand, it is possible to bias the rotatable gear against the main gear 2. For this purpose, a further spring element 14 * in this embodiment, the form of a plate spring, in particular a slotted plate spring to be designated in the broadest sense, be provided. This further spring element 14 has an outer ring 15, from which a plurality of tongues 16, so-called spring tongues, protrude obliquely radially inwardly. These tongues 16 are received by a circumferential groove 17, which is formed in an end portion 18 of the hub 5. By the spring tension thus the further rotatable gear 4 is biased in the axial direction relative to the main gear.
    FIGS. 2 to 5 show an alternative embodiment of the gear arrangement 1 according to the invention. 2 and 3 show side views of the main gear 2 and the rotatable gear 4 in the axial direction 13 (see FIG. 4).
    The main gear 2 has a first surface 19. This first surface 19, also referred to as end face or Axialstirnfläche, is in the assembled state of the gear assembly 1 the rotatable gear 4 opposite, as is apparent from Figs. 4 and 5. In particular, the first surface 19 forms the bottom surface of the recess 12 in which the spring element 7 is arranged. In the radial direction is limited in the embodiment of the gear arrangement 1 according to FIGS. 2 to 5, the recess by the hub 5 and an annular web 20, wherein the annular web 20 is spaced in the radial direction of the hub 5. The rotatable gear 4 is located on the annular web 20 on the main gear 2.
    The rotatable gear 2 has a second surface 21. This second surface 21, also referred to as end face or Axialstirnfläche, is in the assembled state of the gear assembly 1 to the main gear 2 opposite, as shown in FIGS. 4 and 5 can be seen.
    Optionally, the rotatable gear 4 may have an annular web 22, via which it may rest against the annular web 19 of the main gear 2.
    The spring element 7 is thus arranged in the assembled state of the gear arrangement 1 between the first surface 19 of the main gear 2 and the second surface 21 of the rotatable gear 4. 6/19 N2013 / 02900 7
    On the first surface 19 of the main gear 2 and projecting beyond it in the axial direction 13 (FIG. 4) and in the direction of the second surface 21 of the rotatable gear 2, a plurality of first bearing elements 22 are arranged, and in particular integrally formed with the main gear 2.
    On the second surface 19 of the rotatable gear 4 and projecting beyond it in the axial direction 13 (FIG. 4) and in the direction of the first surface 19 of the main gear 2, a plurality of second bearing elements 23 are arranged, and in particular integrally formed with the rotatable gear 4.
    As can be better seen from the detail in FIG. 5, the spring element 7 lies on these first and second support elements 22, 23. In particular, the arrangement of the first and second support elements 22 and 23 on the first surface 19 and the second surface 21 is such that the spring element 7 in the axial direction 13 (Fig. 4) rests exclusively on the first and second support elements 22, 23, so So no contact with the first surface 19 of the main gear and the second surface 21 of the rotatable gear 4 is made.
    In the context of the invention, however, it is also possible for the spring element 7 to be arranged at a distance from the first support elements 22 and / or the second support elements 23. The distance between the first support elements 22 and the spring element 7 can be between 0.1 mm and 2 mm, in particular between 0.2 mm and 1 mm. The distance between the second support elements 22 and the spring element 7 may be between 0.1 mm and 2 mm, in particular between 0.2 mm and 1 mm.
    Although in the following description with respect to the first and second support elements 22, 23 always the majority is used, it is also possible in the invention, however, that in each case only a first and / or a second support element 22, 23 is arranged. However, the arrangement of a plurality of first and / or a plurality of second support elements 22, 23 is the preferred embodiment. 7/19 N2013 / 02900 8
    The first support elements 22 have a first support surface 24 and the second support elements 23 have a second support surface 25 for the spring element 7. It is preferred if the first support surface 24 of the first support elements 22 and the second support surface 25 of the second support elements 23 have a dimension in the radial direction, which is at least as large as the corresponding extent of the spring element 7 in the radial direction in the region of the support.
    In principle, up to twenty, in particular up to ten, that is, for example, two, three, four, five, six, seven, eight, etc., first support elements 22 may be arranged on the main gear. If necessary, however, more than twenty first support elements 22 can be arranged in special cases.
    Likewise, on the rotatable gear 4 up to twenty, in particular up to ten, so for example, two, three, four, five, six, seven, eight, etc., second support elements 23 may be arranged. Likewise, if necessary, more than twenty second support elements 23 can be arranged in special cases.
    According to a preferred embodiment variant, as can be seen in FIG. 2, however, four first support elements 22 are arranged on the main gearwheel 2. These four first support elements 22 may be arranged symmetrically in the circumferential direction 3, ie in particular at right angles to each other. Preferably, a first angle 26, which is formed between two juxtaposed first support elements 22, but not equal to 90 °. The first angle 26 may be selected from a range of 20 ° and 80 °, in particular from a range of 300 and 70 °.
    Particularly preferred is an arrangement in which a first support element 22 in the region of the support web 8 (Fig. 2) on the main gear 2 and a second first support element 22 in the region of the support web 9 (Fig. 3) of the rotatable gear 4 is arranged, in particular when the spring element 7 is a so-called Q-spring. These two first support elements 22 can be angaordnet in the circumferential direction 3 at a distance from the support webs 8, 9, which extends from an angle between 1 ° and 45 °, in particular from an angle N2013 / 02900 8/19 9 between 5 ° and 30 between the support webs 8, 9 and the adjacent these first support elements 22 results. In particular, these two first support elements 22 are arranged next to the open area of the Ω spring in the area below the Ω spring, whereby the Ω spring is better supported in this area.
    According to a further preferred embodiment variant, as can be seen in FIG. 3, three second support elements 23 are arranged on the rotatable toothed wheel 4. These three second support elements 23 may be arranged symmetrically in the circumferential direction 3, ie at an angle of 120 0 to each other. But it is also possible that a second angle 27, which is formed between two juxtaposed second support elements 23, is not equal to 120 0. The second angle 27 may be selected from a range of 60 ° and 115 °, in particular from a range of 80 ° and 110 °.
    Generally, with more than four first and / or second support elements 22, 23, one, two, three or more of the first and / or second support elements 22, 23 are arranged at a distance from the respectively directly adjacent first and / or second support elements 22, 23 which is unequal to the distance between the remaining first and / or second support elements 22, 23. In the extreme case, the first and / or second support elements 22, 23 may be arranged completely randomly on the first surface 19 and the second surface 21, respectively.
    There is also the possibility that the first and second support elements 22, 23 are arranged in the axial direction 13 (FIG. 4) opposite to one another or offset relative to one another on the first surface 19 or the second surface 21. In this case, only one or one of the first and second support elements 22, 23 in the axial direction 13 (FIG. 4) can be arranged opposite one another or offset relative to one another on the first surface 19 or the second surface 21.
    There is also the possibility that the first and / or second support elements 22, 23 are arranged in the radial direction on the same (as shown in FIGS. 2 and 3) or unequal height, wherein also Here, in turn, there is the possibility that only one or individual are arranged in the radial direction at the same or unequal height.
    With regard to the geometric shape, the first and / or second support elements 22, 23 may have any suitable shape. The first and / or second bearing surface 24, 25 may be square, rectangular, round, oval, polygonal, (sickle-shaped) bent, etc., for example.
    In the preferred embodiment, however, the first and / or second support elements 22, 23 - as is apparent from Figs. 2 and 3 - an elongated shape, with a longitudinal extent in a radial direction of the gear assembly 1. However, there is also the Possibility that the support elements 22, 23 are formed running obliquely to the radial direction.
    In this case, a ratio of a length 28 in the radial direction to a width 29 in the circumferential direction 3 of the first and / or second support elements 22, 23 is preferably selected from a range of 2: 1 to 8: 1.
    The first support elements 22 have a first height 30 above the first surface 19 of the main gear 2 in the axial direction 13, as shown in FIG. 5 can be seen. The second support elements 22 have a second height 31 above the second surface 21 of the rotatable gear 4 in the axial direction 13 (FIG. 13).
    The spring element 7 has a wall thickness 32 in the radial direction 13.
    It is advantageous if the sum of first height 30, second height 31 and wall thickness 32 has a value corresponding to a distance x 33 in which the first surface 19 of the main gear 2 is removed from the second surface 21 of the rotatable gear 4 is.
    In general, however, the sum of first height 30, second height 31 and wall thickness 32 may have a value that corresponds to between 50% and 100%, in particular between 90% and 100%, of the distance x 33. It is also possible that at least one but also several of the first support elements 22 and / or second support elements 23 have a first height 30 different from the remaining first support elements 22 and / or second support elements 23, respectively. second height 31 have.
    The first support elements 22 may have a first height 30 above the first surface 19, which is selected from a range of 0.05 mm to 1 mm, in particular selected from a range of 0.1 mm to 0.8 mm.
    The second support elements 23 may have a second height 31 above the second surface 21, which is selected from a range of 0.05 mm to 1 mm, in particular selected from a range of 0.1 mm to 0.8 mm.
    Furthermore, it is possible for the first height 31 of the first support elements 22 to be identical or different from the second height 32 of the second support elements 23.
    It is also possible that the support elements 22 and / or 23 and / or the spring element 7 is at least partially, in particular in the region of the support of the spring element 7 on the support elements 22, 23, provided with a sliding coating or are. For example, this lubricious coating may be formed from a lubricating varnish.
    A sliding coating in the sense of the invention is a coating with which the friction of abutting surfaces is reduced.
    The layer thickness of the sliding coating can be taken into account with respect to the above-described sum of first height 30, second height 31 and wall thickness 32 with respect to the distance x 33.
    In the preferred embodiment, the main gear 2 and the rotatable gear 4 are made of a metallic sintered material. This is particularly the case since the shaping of the first and second support elements 22, 23 in series is relatively easy to implement. It should be noted, however, that the 11/19 N2013 / 02900 12
    Main gear 2 and / or the rotatable gear 4 may also consist of a solid material.
    In particular, with regard to the sintering production, it proves to be an advantage if the first support elements 22 and / or second support elements 23 has no sharp-edged transitions between adjoining surfaces. Thus, for example, starting from the first surface 19 in the direction of the first support surface 24 of the first support elements 22 oblique ramps may be formed, as shown in FIG. 5 can be seen. Likewise, starting from the second surface 21 in the direction of the second bearing surface 25 of the second bearing elements 23, such inclined ramps may be formed.
    Furthermore, radial end regions of the elongate first and / or second support elements 22, 23 may be designed with a rounding, as can be seen from FIGS. 2 and 3.
    With all these measures, the demolding of the main gear 2 and the rotatable gear 4 can be improved, whereby the first and second support elements 22, 23 are not destroyed during molding.
    To secure the relative axial position of the rotatable gear 4 with respect to the main gear 2, a securing element 34, in particular a securing ring, may be provided, as shown in Fig. 4. The securing ring can be held in a corresponding, in particular groove-shaped, receptacle 35.
    But it is also possible or preferred that the rotatable gear 4 is biased in the axial direction against the main gear 2. For this purpose, instead of the securing element 34 in the receptacle 35, a further spring element can be arranged, for example the above-mentioned further spring element 14 (see FIG. 1). By biasing the twisting or twisting of the spring element 7, with which the rotatable gear 4 is biased in the circumferential direction 3 relative to the main gear 2, better avoided or prevented. 12/19 N2013 / 02900 13
    By biasing the dynamic behavior of the gear assembly 1 is changed by this carrier is due to higher friction.
    For the sake of order, it should finally be pointed out that, for a better understanding of the construction of the gear arrangement 1, these or their components have been shown partially unevenly and / or enlarged and / or reduced in size. N2013 / 02900 13/19
    LIST OF REFERENCE NUMBERS
    gearing
    main gear
    circumferentially
    gear
    hub
    recess
    spring element
    supporting web
    supporting web
    end
    end
    recess
    direction
    spring element
    ring
    tongue
    groove
    end
    surface
    ring land
    surface
    support element
    support element
    bearing surface
    bearing surface
    angle
    Angle length
    Width height height
    Wall thickness
    distance
    fuse element
    Recording 14/19 N2013 / 02900
    权利要求:
    Claims (9)
    [1]
    1 gear arrangement (1) 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 ), and wherein the main gear (2) has a first surface (19) and the rotatable gear (4) has a second surface (21), and a spring element (7) disposed between the first surface (19) of the main gear (2) and the second surface (21) of the rotatable gear (4) is arranged, and with which the rotatable gear (4) in the circumferential direction (3) is biased against the main gear (2), characterized in that the main gear (2 ) on the first surface (19) at least one, in particular a plurality of, over this first surface (19) in the direction of the second surface (21) of the rotatable gear (4) projecting (s) support element (s) (22 ) and the rotatable gear (4) at least one, ins have a plurality of, on this second surface (21) in the direction of the first surface (19) of the main gear (2) projecting (s) second (s) support element (s) (23), wherein the spring element (7) between the or the first and the second support element (s) (22, 23) and thus spaced from the first surface (19) of the main gear (2) and the second surface (21) of the rotatable gear (4) is arranged.
    [2]
    2. gear arrangement (1) according to claim 1, characterized in that at least three second support elements (23) are arranged.
    [3]
    3. gear arrangement (1) according to claim 1 or 2, characterized in that at least four first support elements (22) are arranged.
    [4]
    4. gear arrangement (1) according to one of claims 1 to 3, characterized in that the one or more first and / or the second or the Aufla- 15/19 N2013 / 02900 2 geelement (s) (22, 23) are elongated with a longitudinal extent in a radial direction of the gear arrangement (21).
    [5]
    5. gear arrangement (1) according to claim 4, characterized in that a ratio of a length (28) to a width (29) of the first and / or of the second support elements (s) (22, 23) is selected from a range of 2: 1 to 8: 1.
    [6]
    6. gear arrangement (1) according to claim 1 to 5, characterized in that the spring element (7) is designed as Ω spring and in each case a first support element (22) is arranged in the region adjacent to the open area of Ω spring.
    [7]
    7. gear arrangement (1) according to one of claims 1 to 6, characterized in that the first surface (19) of the main gear (2) and the second surface (21) of the rotatable gear (4) with a distance x (33) from each other wherein a first height (30) of the at least one first support element (22), a second height (31) of the at least one second support element (23) and a wall thickness (32) of the spring element (7) in the axial direction (13) the gear arrangement (1) in total between 50% and 100% corresponds to the distance x (33).
    [8]
    8. gear arrangement (1) according to one of claims 1 to 7, characterized in that the support elements (22, 23) and / or the spring element (7) is at least partially provided with a lubricious coating or are.
    [9]
    9. gear arrangement (1) according to one of claims 1 to 8, characterized in that the rotatable gear (4) with a further spring element in the axial direction (13) is biased against the main gear (2). 16/19 N2013 / 02900
    类似技术:
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    同族专利:
    公开号 | 公开日
    US20140224053A1|2014-08-14|
    CN103982621B|2017-10-24|
    US9482334B2|2016-11-01|
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    DE10056133A1|2000-11-13|2002-05-23|Zf Lenksysteme Gmbh|Electrical steering device for motor vehicles has worm wheel in elastic compensation coupling|
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    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|
    AT517424B1|2015-06-25|2019-09-15|Miba Sinter Austria Gmbh|Device for releasing play of meshing gears of a gear drive|
    AT517484B1|2015-10-06|2017-02-15|Metaldyne Int Deutschland Gmbh|gearing|
    US10508727B2|2016-08-31|2019-12-17|Spx Flow, Inc.|Drive system and drive sub-assembly for driving a shaft|
    FR3065267A1|2017-04-18|2018-10-19|Airbus Helicopters|GEARED GEAR WHEEL, GEAR DEVICE, POWER TRANSMISSION BOX AND AIRCRAFT HAVING A ROTATING VESSEL|
    DE102017208800B3|2017-05-24|2018-10-31|Zf Friedrichshafen Ag|Gear for a planetary gear|
    JP6800095B2|2017-06-16|2020-12-16|川崎重工業株式会社|gear|
    DE102017217397A1|2017-09-29|2019-04-04|Aktiebolaget Skf|Bearing arrangement which is equipped with a rolling bearing and a Schernenzahnrad, in particular for a balance shaft|
    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
    ATA50098/2013A|AT513613B1|2013-02-08|2013-02-08|gearing|ATA50098/2013A| AT513613B1|2013-02-08|2013-02-08|gearing|
    CN201410014145.7A| CN103982621B|2013-02-08|2014-01-13|Geared system|
    DE102014101111.2A| DE102014101111A1|2013-02-08|2014-01-30|gearing|
    US14/174,921| US9482334B2|2013-02-08|2014-02-07|Gearwheel arrangement|
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