• 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 first component (3) having a toothing and a second component (4) arranged therein, wherein first projections (8) are formed below the toothing (6), between which gaps (17) are formed are arranged, the second component (4) second projections (18) which engage in these gaps (17), and wherein between the first component (3) and the second component (4) an elastomeric ring with a plurality of deformation elements (22 ) is arranged, whose base body (20) between the toothing (6) and the first and second projections (8, 18) is arranged and the deformation elements (22) between the first projections (8) and the second projections (18) engage, and wherein the deformation elements (22) each have at least one release (35) or in each case at least one raised region and / or that the first component (3) and / or the second component (4) in the region of A nlage the deformation elements (22) on the first and / or second projections (8, 18) in their contact surfaces exemptions (36).
    公开号:AT516397A4
    申请号:T50841/2014
    申请日:2014-11-19
    公开日:2016-05-15
    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 first component and a second component, wherein the first component has a toothing and below the toothing in the axial direction protruding first projections, between which gaps are formed, the second component is at least partially disposed within the first component and In the axial direction projecting second projections which engage in the gaps between the first projections of the first component, and wherein between the first component to the second component at least one elastically deformable element is arranged.
    To avoid the vibration excitation in the torque transmission by means of gears, it is known from the prior art to use elastically deformable elements. Thus, e.g. the AT 501 915 A4 a device for torsionally elastic torque transmission between a shaft and mounted on the shaft, a sprocket and a hub forming gear with two on the one hand the shaft and on the other hand the ring gear rotatably associated coupling parts having mutually projecting, staggered claws, and arranged between the claws, elastomeric damping bodies, wherein the two coupling parts are supported on the damping body exclusively in the circumferential direction and the ring gear is mounted on the hub in the radial direction unyielding with respect to the shaft. Since the gap between the jaws of the two coupling parts is filled with an elastomeric material, torsional vibrations occurring between the toothed rim and the hub are damped by the elastomeric intermediate layer between the opposite flanks of the intermeshing claws. Due to the unyielding storage of the ring gear in the radial direction any additional vibrations that may occur can be adversely affected on the meshing.
    The principle of elastic torque transmission is also used in the area of balance shafts in drives. For example, DE 10 2011 018 771 A1 describes a motor vehicle device for an internal combustion engine, with at least one crankshaft, with at least one first gear, which is non-rotatably connected to the crankshaft, with at least one balance shaft, which is intended to reduce at least torsional vibrations of the internal combustion engine with at least one second gear rotatably connected to the balancer shaft and operatively connected to the first gear, and at least one decoupler provided for coupling the first gear from the at least one crankshaft and / or the second gear from the first gear to decouple at least one balance shaft torsionally elastic.
    It is further known that in such gear arrangements, the elastomeric element acts not only in the circumferential direction but also in the radial direction. For example, DE 101 16 236 A1 describes a toothed wheel comprising an inner part and an outer part provided with teeth on the outer circumference, wherein the outer part surrounds the inner part at a radial distance on the outer peripheral side and wherein in the gap formed by the gap at least one spring body made of an elastomeric Material is arranged. The spring body may be substantially wave-shaped, circumferentially closed in itself, be formed, wherein the inner part evenly distributed in the circumferential direction, radially outwardly facing first projections, that the outer part uniformly distributed in the circumferential direction, radially inwardly facing second projections, and the Number of the first projections of the number of second projections corresponds and the first and second projections overlap each other in the radial direction. For transmitting power, the mutually facing, circumferential flanks of the projections of inner part and outer part are supported in the circumferential direction by means of the elastomeric material of the spring body disposed therebetween, so that the elastomeric material is exposed to only one pressure bias in this area. It is thus achieved that the Fe derkörper damaged by an undesirably high shear stress and / or destroyed if the forces to be transmitted are too large. The gear wheel thus has runflat on, since even with damaged and / or destroyed spring body, the power transmission between the inner part and the outer part is not interrupted, as supported by the overlap of the projections in the radial direction, the projections to each other and thereby ensures the power transmission.
    It is the object of the invention to improve the aforementioned gear arrangement with respect to the torque transmission.
    This object of the invention is achieved in the gear arrangement mentioned above in that the at least one elastically deformable element of elastic deformation in the circumferential direction opposes a different resistance than in the radial direction.
    The advantage here is that - as known per se - vibrations can be absorbed during the torque transmission via the at least one elastic element, but damping can take place not only in the circumferential direction but also in the radial direction, the damping being in the radial direction configured differently, so that the gear assembly can be easily adapted to various applications in terms of their damping properties. Due to the different stiffness of the at least one elastic element in the radial direction and in the circumferential direction of the gear arrangement, despite the possibility of vibration damping in both directions of the gear arrangement, a higher security against failure can be achieved by overloading the at least one elastic element. Thus, the gear assembly can better absorb pulses that can excite vibration in the direction that they are normally expected in a particular application. Although the damping can be better absorbed by the damping in the second direction, the at least one elastic element can have a higher strength in it, which improves the stability of the gear arrangement in this direction and thus allows higher forces to be absorbed.
    According to an embodiment of the gear arrangement, it may be provided that the elastically deformable element opposes a different resistance in the circumferential direction and in the clockwise direction than in an elastic deformation in the circumferential direction and in the counterclockwise direction. In other words, the elastic element of a deformation in the direction of rotation opposes a different resistance than against the direction of rotation. The advantage here is that so that the elastically deformable element is better adapted to the expected mechanical loads, so on the one hand this can have a higher mechanical load in the direction of rotation, and at the same time but also an elastic element with corresponding damping properties can be provided.
    It can further be provided that the first component below the toothing in the axial direction has protruding first projections, between which gaps are formed, further that the second component in the axial direction projecting second projections, which in the gaps between the first projections of the first Engage component and that the at least one elastically deformable element at least partially engages between the first projections of the first component and the second projections of the second component and in the region of engagement has exemptions. By these exemptions, the different stiffness of the at least one elastic element in the radial and circumferential direction can be easily provided by the material of the at least one elastic element can escape in a stress in these exemptions. It is thus possible that the at least one elastic element with respect to its composition, i. with regard to the material used, can be maintained unchanged in order to achieve the desired stiffness behavior. In addition, it is advantageous that the size of the recesses and the extent of rigidity in the two directions can be easily adapted to different applications.
    According to one embodiment variant, provision can be made for the exemptions to be designed as breakthroughs. It is possible, the areal
    To reduce expansion of the exemptions or to increase the difference in stiffness behavior of at least one elastic element in the two directions with the same areal extent.
    The exemptions may alternatively or additionally also be formed or arranged in the first component and / or in the second component in the region of the abutment of the at least one elastically deformable element. It can thus also be achieved that the at least one elastic element can escape during a corresponding mechanical stress during the torque transmission in these exemptions, and thus opposes the at least one elastic element in the two directions of deformation a different resistance.
    In the preferred embodiment, the at least one elastically deformable element is formed as an elastomeric ring with deformation elements. This can be easily manufactured with respect to the different stiffnesses and, moreover, the assembly of the gear arrangement can be made simpler. In addition, the elastomeric ring does not necessarily require changes in the first and second components of the gear assembly to achieve the functionality of the different stiffnesses of the at least one elastomeric member.
    In this case, the elastomer ring preferably consists of a single elastomer. It is thus achievable a further simplification of the Fierstellung the gear assembly. The different stiffness of the elastomeric ring in the two directions given can preferably be achieved by geometric design. It can therefore be dispensed deposits, mixtures of the elastomer with less elastic elements, etc., whereby the at least one elastic element of the gear arrangement can be produced more cheaply. In particular, it is not necessary to pay attention to material compatibility or premature aging of the at least one elastomeric element due to a further material contained in this can be avoided. Likewise, compound problems, e.g. a filled with a filler material for stiffening elastomer is not important. The at least one elastomeric element can thus be made more reliable.
    According to another embodiment of the gear arrangement can be provided that a plurality of elastically deformable elements are arranged, which are formed as plate-shaped springs, wherein the springs are oriented in the radial direction. In comparison with the elastomer ring, although the assembly of the gear arrangement is thus more complex, however, this embodiment offers the advantage that if one of the elastically deformable elements is damaged, the others can still fulfill their function completely.
    As a result, a higher reliability with corresponding emergency running properties can also be achieved. In addition, in the case of a spring break only the damaged spring must be replaced and not the entire system of vibration damping itself.
    According to a further embodiment variant, it can be provided that the springs engage in receptacles in the first component and in receptacles in the second component. It is thus a simple integration of the elastically deformable elements in the gear arrangement achieved and also the assembly of the gear arrangement can be simplified by the elastically deformable elements must be inserted only in the receptacles in the axial direction.
    Preferably, the resistance, which opposes the at least one elastically deformable element of an elastic deformation in the circumferential direction, is smaller than the resistance, which opposes the at least one elastically deformable element of an elastic deformation in the radial direction. It can thus vibration excitations, which are caused by a shaft on which the gear assembly is arranged, or by a meshing with the gear assembly further gear be attenuated on the one hand, on the other hand, the meshing engagement with the other gear can be improved in accuracy by the Teeth of the gear arrangement with respect to the teeth of the other gear is true to the track or remains.
    It is further preferred if the second component is guided with an end-side surface on the first component. It is thus created a mechanical failover in the event of failure of the at least one elastically deformable element, so that further damage to other components, e.g. a drive train of a vehicle can prevent or these can be prevented.
    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:
    1 shows a first embodiment of a gear arrangement oblique view in exploded view;
    2 shows the application of a gear arrangement in a mass balance in a sectional view.
    3 shows a second embodiment of the gear arrangement in axial view;
    4 shows a section through the gear arrangement according to FIG. 3 in oblique view;
    Fig. 5 shows the representation of the gear arrangement according to Fig. 4 with attached covers.
    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 these position information in a change in position mutatis mutandis to transfer to the new location.
    1 and 2, a first embodiment of a gear arrangement 1 and its application in a mass balance 2 for a drive train in a motor vehicle are shown.
    The gear arrangement 1 comprises a first, radially outer component 3, a concentrically arranged second, radially inner component 4 and an elastically deformable element 5 or consists of these elements. The first, radially outer component 3 has on a front side a toothing 6 in the form of a spur toothing.
    This toothing 6 may have a form adapted to the particular application of the gear arrangement 1 shape, for example, for the formation of a transmission gear. But there are also other forms of teeth 6, for example, a helical toothing, etc. possible. Furthermore, the toothing 6 can extend in an axial direction 7 of the toothed wheel arrangement 1 over the entire width of the first, outer component 3 or only over a partial area of this width.
    The second component 4 is arranged at least partially within the first component 3. The at least one elastically deformable element 5 is arranged between the first component 3 and the second component 4.
    It should be noted that the terms "radially outer" and "radially inner" do not necessarily mean that the first component 3 with respect to the second component 4 entirely radially above the latter and the second component 4 with respect to the first component 3 in its entirety are arranged radially below the latter, as can be seen from Figs. 1 and 2. Rather, there is the possibility of an "overlap area".
    The second, radially inner component 4 may also be referred to as a hub part and the first, radially outer component 3 as a toothed ring.
    The first, radially outer component 3 has below the toothing 6 in the axial direction 7 projecting first projections 8 (cams), which are in particular formed integrally with the first, radially outer component 4. In the illustrated embodiment of the gear arrangement 1, four such first projections 8 are arranged or formed. It should be noted, however, that this number of first protrusions should not be understood as limiting. It is also possible for fewer or more such first projections 8 to be arranged or formed on the first, radially outer component 3.
    The first projections 8 are arranged or formed to form a distance 9 to a bottom 10 of the toothing 6. For this purpose, the first, radially outer component 3 has an annular end wall 11, which adjoins the toothing 6 and extends radially inwards. The first projections 8 are formed on this annular end wall 11. The first projections 8 extend from an inner surface 12 of the annular end wall 11 in the direction of an inner surface 13 of a likewise annular end wall 14 of the second, radially inner component 4. The first projections 8 have an approximately trapezoidal cross-section in the direction of the axial direction 7 or are formed like an annular ring, but may also have a different cross-section. The first projections 8 preferably have a height 15 above the surface 12 of the annular end wall 11, ie in the axial direction 7, the maximum width 16 of the gear arrangement 1 in the axial direction 7 minus the thickness of the end wall 11 of the first, radially outer Component 3 and minus the width of the end wall 14 of the second, radially inner component 4 corresponds.
    Gaps 17 are formed between the first projections 8 of the first, radially outer component 3.
    The second, radially inner component 4 is arranged at least partially, in particular entirely, within the first, radially outer component 3. On the inner surface 13 of its annular end wall 14, the first, radially inner component 4 has second projections 18 (cams). The second projections 18 extend from the inner surface 13 of the annular end wall 14 in the axial direction 7 toward the inner surface 12 of the annular end wall 11 of the first, radially outer component 3. Further, the second projections 18 of the second, radially inner Component 4 is arranged in the gaps 17 between the first projections 8 of the first, radially outer component 3.
    Preferably, the second projections 18 are at least approximately, in particular exactly, arranged at the same radial height as the first projections 8.
    The size and shape of the second protrusions 18 preferably correspond to those of the first protrusions 8. The second protrusions 18 may also have a shape and / or size different from the size and shape of the first protrusions 8.
    In the illustrated embodiment, four second projections 18 are arranged on the second, radially inner component 4. However, the number of second projections 18 may also differ therefrom. It can therefore be arranged 18 more or less second projections. In the preferred embodiment of the gear arrangement 1, however, the number of first projections 8 is equal to the number of second projections 18, so that in each gap 17 between the first projections 8 in each case a second projection 18 is arranged.
    The gaps 17 between the first projections 8 are larger in a circumferential direction 19 than the extension of the second projections 18 in the circumferential direction 19, so that the second projections 18 at least on one side, preferably on both sides, (with respect to the circumferential direction 19) with formation of distances from stands to the first projections 8 are arranged. At least one elastically deformable element 5 is arranged at these distances, wherein at least a part of the elastically deformable element 5 is arranged between each first projection 8 and each projection 18.
    The at least one elastically deformable element 5 is preferably formed annularly as an elastomeric ring, as shown in Fig. 1. For this purpose, the elastically deformable element 4 has a, in particular closed, annular basic body 20. A width 21 of the base body 20 in the radial direction is dimensioned so that it is not greater than the distance 9 between the bottom 10 of the toothing 6 of the first, radially outer component 3 and the top of the bottom 10 facing top of the first projections eighth Thus, the annular base body 20 between the toothing 6 and the first projections 8 are arranged, as shown in FIG. 2 can be seen. After the second protrusions 18 of the second, radially inner component 4 are arranged at least approximately, in particular precisely, at the same radial height as the first protrusions 8, the base body 20 can also be arranged above the second protrusions 18 in the radial direction. Preferably, the base body 20 of the elastically deformable element 5 rests against the underside 10, the first projections 8 and the second projections 18, as can also be seen in FIG. 2.
    The main body 20 may have an at least approximately square, an at least approximately rectangular, an at least approximately round or at least approximately oval cross-section. Other cross-sectional shapes are also possible.
    A plurality of deformation elements 22 are arranged on the base body 20, projecting radially inwards beyond it. In the embodiment of the gear arrangement 1 shown in FIG. 1, eight such deformation elements 22 are arranged, in particular formed in one piece with the base body 20.
    These deformation elements 22 protrude into the spaces between the first projections 8 and the second projections 18, so that therefore the first projections 8 are separated from each other by the deformation elements 22 from the second projections 18 in the circumferential direction 19. After eight such deformation elements 22 are arranged, these lie in the circumferential direction 19 viewed on both sides of the first projections 8 and the second projections 18 at.
    The deformation elements 22 have a height 23 in the radial direction, which is dimensioned such that the deformation elements end at the level of radially lower undersides 24, 25 of the first projections 8 and the second projections 18.
    There is also the possibility, although not preferred, that the deformation elements 22 end in the radial direction above the lower sides 24, 25 of the first and second projections 8, 18.
    Next there is also the possibility, which is also not preferred that only four such deformation elements 22 are present, and thus the first projections 8 with a pointing in the circumferential direction 19 end face on the corresponding opposite end face of the second projections 18 abut gene.
    In general, however, it is preferred if the number of deformation elements 22 is twice as large as the number of first projections 8 or second projections 18.
    According to a further embodiment, there is the possibility that the deformation elements 22 are loosely inserted between the first projections 8 and the second projections 18, that is not formed on the base body 20 or generally no base body 20 is present.
    The first, radially outer component 3 and / or the second, radially inner component 4 are preferably made of a metallic material, for example of a steel, preferably of a sintered material, for example a sintered steel. However, it is also possible to use other metallic materials for the first, radially outer component 3 and / or the second, radially inner component 4, wherein the first, radially outer component 3 and / or the second, radially inner component 4 also comprise at least two different metallic materials can exist.
    The at least one elastic deformable elements 5 consists at least partially, in particular entirely, of at least one rubber-elastic material, for example of an (X) NBR ((carboxylated) acrylonitrile-butadiene rubber), HNBR (hydrogenated nitrile rubber), a silicone rubber. Rubber (VMQ), NR (natural rubber), EPDM (ethylene-propylene-diene rubber), CR (chloroprene rubber), SBR (styrene-butadiene rubber), etc., where again material mixtures can be used.
    By "at least partially" is meant that in the at least one elastically deformable element 5, e.g. Stiffening elements, e.g. Fibers and / or threads, for example of metal, plastic, natural fibers, etc., or rods, etc. may be incorporated. Preferably, however, the at least one elastic deformable elements 5 consists exclusively of a rubber-elastic material. But particularly preferably, the at least one elastic deformable elements 5 consists of a single elastomer. Via the at least one elastically deformable element 5, vibration excitations, which are transmitted from the second component 4 into the first component 3 or from the first component 3 into the second component 4, can be damped. In particular, this allows peak pulses of second component 4 to be intercepted onto first component 3 or from first component 3 to second component 4 on a case-by-case basis.
    As can be seen from the application example shown in FIG. 2, the gear arrangement 1 can be arranged on an imbalance element 26. For this purpose, the end walls 11, 14 of the first component 3 and of the second component 4 have an axial recess 27, in particular a bore. The recess 27 of the second, radially inner component 4 has a smaller diameter, that is, the recess 27 of the first, radially outer component 3. Thus, the gear assembly 1 sits on the second, radially inner component 4 on a hub portion 28 of the unbalance element 26 and is connected via this with the imbalance element 26. For this purpose, the second, radially inner component 4 has an annular web 29 projecting from the annular end wall 14 in the axial direction 7. This annular web 29 also extends through the recess 27 of the first, radially outer component 3, wherein the latter rests with the annular end wall 11 on the annular web 29.
    It should be noted that the second projections 18 of the second, radially inner component 4 are preferably formed on the annular web 29.
    It should also be mentioned that the gear arrangement can also be arranged on a shaft without unbalance element 26 via the recess 27.
    After the second projections 18 of the second, radially inner component 4 end in the radial direction below a radial end face 30 of the annular end wall 14, and the second component 4 with the radial end face 30 preferably bears against the first component 3 on the underside 10 of the toothing 6 , is formed between these a cavity 31 for receiving the main body 20 of the elastomeric ring.
    The imbalance element 26 may in turn have a recess 32, in particular a bore, for arrangement on a shaft.
    Such imbalances are used in particular in balance shafts of internal combustion engines.
    To form the imbalance, the imbalance element 26 has an uneven mass distribution, which is achieved by the formation of an imbalance mass 33, wherein this imbalance mass 33 is arranged or formed only over a portion of the circumference of the imbalance element 26.
    The gear arrangement 1 is preferably arranged with the interposition of a ring element 34 on the Umwuchtelement 26, wherein the ring member 34 abuts the unbalanced mass 33 on the one hand and on the gear wheel arrangement 1 on the other.
    The at least one elastically deformable element 5 opposes an elastic deformation in the circumferential direction 19 to a different resistance than in the radial direction. In other words, the at least one elastic member 5 has a different rigidity in the circumferential direction than in the radial direction. Since at least one elastic element 5 has a direction-dependent stiffness.
    In the embodiment of the at least one elastic element 5 as deformation elements 22 or as elastomer ring with the deformation elements 22, this can be achieved, for example, by using elastomers of different stiffness for producing the deformation elements 22 or the elastomer ring with the deformation elements 22. Alternatively or additionally, stiffening elements, such as e.g. Fibers or platelets or spring plates are incorporated in a preferred orientation in the at least one elastomer.
    However, since this is correspondingly expensive in the production of the at least one elastic element 5, this is preferably made of only a single elastomer and thus consists only of a single elastomer.
    In this case, it is provided that the at least one elastic element 5 has exemptions 35. It is thus achieved that the elastomer can escape more easily in a mechanical stress in these exemptions 35, as in areas without exemptions 35.
    In the embodiment of the gear arrangement 1 according to FIG. 1, these exemptions are formed as depressions in the deformation elements 22. Specifically, these recesses substantially have the cross-sectional shape - viewed in the axial direction 7 - the deformation elements 22, but are made smaller in area, so that they are surrounded by a raised edge.
    However, this form should not be understood as limiting. Rather, these depressions can also have other cross-sectional shapes - viewed in the axial direction 7 - have. For example, they may be round, oval, rectangular, square, triangular, or generally polygonal, etc., be formed.
    But there is also the possibility of reversal, i. that no depressions are arranged or formed on the deformation elements 22, but raised areas. Likewise, both raised and recessed areas can be arranged or designed. Furthermore, more than one of these recessed and / or raised areas per deformation elements 22 may be arranged. Further, these recessed and / or raised portions are preferably on both sides - viewed in the axial direction 7 - arranged or formed on the deformation elements 22, wherein according to another Ausfüh tion variant, these raised and / or recessed areas on the two sides may have a different shape. It is also possible for a plurality of recessed and / or raised regions to be formed or arranged on one side of the deformation elements 22 with a different shape. The exact placement of these exemptions 35 or raised areas can be selected or adapted to the respective application of the gear arrangement 1.
    Additionally or alternatively, it is possible that (also) the base body 20 of the elastomeric ring is provided with such exemptions 25 and / or raised areas.
    The exemptions 35 are preferably already taken into account and formed during the production of the deformation elements 22 or of the elastomer ring with the deformation elements or in general of the at least one elastic element 5. However, it is also possible for their subsequent production, for example by means of cutting methods, such as. Milling.
    According to a further embodiment of these exemptions 35, these can also be formed as openings through the deformation elements 22 and / or the main body 20 of the elastomeric ring with the deformation elements 22 or generally by the at least one elastic element 5. These openings are preferably formed in the axial direction 7. It is further preferred if the apertures have a shape which has a greater extent in the radial direction than in the circumferential direction 19, that is, for example, are formed as ovals oriented in the radial direction.
    Alternatively, or in addition to the exemptions 35 or raised areas in the at least one elastic element 5, according to another embodiment variant of the gear arrangement 1, it is possible to provide reliefs 36 in the first protrusions 8 of the first component 3, as shown in FIG 1 is shown by dashed lines on the basis of a first projection 8. It should be noted, however, that all the first projections 8 have such exemptions 36.
    These exemptions 36 are preferably formed in the abutment surfaces of the at least one elastic element 5 on the first projections 8, wherein it is further preferred if these exemptions 36 are arranged or formed in the circumferential direction 19 on both abutment surfaces for the at least one elastic element 5 ,
    With regard to shape, number and Fierstellung these exemptions 36 reference is made to the above statements on the exemptions 35 in the at least one elastic element 5.
    Alternatively or additionally, there is the possibility that the second projections 18 of the second component 4 have such exemptions 36, even if this is not shown in Fig. 1.
    The at least one elastic element 5 made of the elastomer can be connected to the first and / or second component 3, 4, for example by being glued.
    There is also the possibility that this is vulcanized or that the connection takes place exclusively by friction. The connection can be made, for example, with the underside 10 of the toothing 6 and / or with the first and / or second projections 3, 4. In order to improve the connection formation, there is also the possibility that the surfaces to be joined are roughened, for example by (sand) blasting or by grinding, etc.
    Preferably, all edges of the elastomeric ring with the deformation elements 22 and the deformation elements 22 are provided with curves.
    According to another embodiment of the gear arrangement 1, it can be provided that the elastically deformable element 5 opposes an elastic deformation in the circumferential direction 19 and in the clockwise direction to a different resistance than an elastic deformation in the circumferential direction 19 and counterclockwise. In particular, the elastic element 5 in the direction of rotation of the gear assembly 1, that is, for example, clockwise, a higher stiffness, as in the opposite direction, that is, for example, counterclockwise. This can be achieved, for example, by virtue of the fact that the reliefs 35 have a corresponding geometry, for example a cross section which decreases in the direction of the higher rigidity. Also, the higher rigidity in the positive circumferential direction 19 as compared to that in the negative circumferential direction 19 (in the clockwise direction) can be achieved by the corresponding arrangement of the above-described stiffening elements.
    It is also possible that in the positive circumferential direction 19 in comparison to the in the negative circumferential direction 19 different, in particular higher, resistance, the elastic member 5 opposes a deformation, via a corresponding geometry of the exemptions 36 in the projection 8 or the Projections 8 of the radially outer component 3 is achieved. For example, the exemptions 36 which rest in the circumferential direction 19 in the clockwise direction on the elastic element 5 may have a smaller volume than the exemptions 36 which rest in the circumferential direction 19 and counterclockwise on the elastic element 5. Thus, in the circumferential direction 19 and in the clockwise direction, the deflection of the elastic element 5 is less available under load than in the opposite direction.
    Moreover, it is possible that in the circumferential direction 19 only every second projection 8 is executed with an exemption 36, so that the elastic element 5, for example, at a stress in the circumferential direction 19 abuts a projection 8 with at least one release 36 and at Stress against the circumferential direction of a projection 8 without such exemption 36 is applied.
    Furthermore, to achieve this effect it can be provided that the release 35 is formed in the elastic element 5 in the center of the projections 8.
    It may also be provided to achieve this effect that are arranged on radial fleas of the projections 8 between the deformation elements 22 of the elastic element 5 intermediate elements. These can also be connected to the projections 8 or the deformation elements 22 or, in general, to the elastic element 5. In order to achieve the different stiffness in the counterclockwise direction, these intermediate elements may be alternately formed in the circumferential direction 19 of a different hard material and / or these intermediate elements may be performed in the circumferential direction 19 alternately with a first width and a relatively smaller width ,
    Further, in order to achieve this effect that the elastic member 5 counteracts a different resistance in the circumferential direction 19 of deformation in the counterclockwise direction, it can be provided that the elastic member 5 in the circumferential direction 19 alternately arrange elastic deformation members 22 provided with at least one first release 35 are provided, and elastic deformation elements 22, which are provided with no or one of the first exemption 35 smaller exemption 35 has.
    FIGS. 3 to 5 show a further embodiment of the gear arrangement 1, which is possibly independent of itself, wherein the same reference numerals or component designations are used again for the same parts as in the preceding FIGS. 1 and 2. In order to avoid unnecessary repetition, reference is made to the detailed description of FIGS. 1 and 2.
    The gear arrangement 1 according to FIGS. 3 to 5 likewise has the first component 3 and the second component 4, wherein the second component 4 is arranged below the first component 3 in the radial direction.
    The first component 3 has the toothing 6 on the outer circumference.
    Unlike the first embodiment described above, the two components 3, 4 but not in the axial direction 7 projecting projections 8, 18 and also has the first component 3 at all no such projections.
    The second component 4 has a plurality of projections 37 protruding in the radial direction. In the specific embodiment, six projections 37 are provided, but this number is not to be understood as limiting. The pros
    Jumps 37 are arranged on the outer circumference of an annular base body 38 or integrally formed therewith. Like the first and second projections 8, 18 described above, the projections 37 are formed in the manner of a circular ring segment, and the gaps 17 are formed between the projections 37. In these gaps 17 each have a spring 39 is arranged. But there may also be more than one spring 39 per gap 17.
    The gear arrangement 1 therefore has a plurality of elastically deformable element 5.
    The springs 39 are preferably formed plate-shaped, wherein the longer narrow side, as can be seen from Figures 3 and 4, is preferably oriented in the radial direction, so that the springs 39 are thus arranged vertically.
    In other words, the narrow sides point in the axial direction.
    It should be noted that the gear arrangement 1 can also have a mixture of the two variants, that is to say both at least one of the elastically elastically deformable elements 5 and springs 39.
    There is the possibility that the springs 39 are connected to the two components 3, 4, for example welded. In the preferred embodiment, however, the springs 39 are on the one hand in, in particular slot-shaped, receptacles 40 in the bottom 10 of the toothing 6 of the first, radially outer component 3, and on the other hand, in particular slot-shaped, recesses 41 on a radially outer top 42 of the body 38th of the second, radially inner component 3 is arranged with its ends, the middle parts of the springs 37 preferably remaining freely deformable in the gaps 17. This embodiment variant has the advantage that the springs 39 for connection to the two components 3, 4 simply have to be inserted into the corresponding receptacles 40, 41. In addition, however, a connection of the springs 39 with the receptacles 40, 41 can also take place in this embodiment variant, for example by gluing to the receptacles 40, 41.
    Preferably, in each case one receptacle 40 and one receptacle 41 lie opposite one another in the radial direction.
    It is also achieved with this embodiment of the gear arrangement that the elastically deformable elements of the deformation oppose a direction-dependent resistance.
    In general, in all embodiments of the gear arrangement, the resistance which the at least one elastically deformable element 5 opposes in the circumferential direction to elastic deformation is less than the resistance which the at least one elastically deformable element opposes to elastic deformation in the radial direction, i. the at least one elastic element is stiffer in the radial direction than in the circumferential direction. It is thus achieved on the one hand the damping effect described above, on the other hand can thus the running accuracy of the gear assembly 1 despite the existing elastically deformable elements 5 can be improved.
    The first, radially outer component 3 may further comprise at least one, in particular two, end face (s) - viewed in the axial direction 7 - a deposition 43 for receiving a ring element 44.
    It is further preferred in all embodiments, when the second component 4 is guided with an end-side surface on the first component 3. This is in the first embodiment of the gear arrangement 1 according to FIG. 1 via the end face 30 of the annular end wall 14, which rests against the first, radially outer component 3, and in the embodiment of the gear arrangement 1 according to FIGS System of the projections 37 on the underside 10 of the toothing 6 of the first, radially outer component 3 achieved.
    The gear arrangement 1 has the advantage of a mechanical safety device if the at least one elastically deformable element 5 fails as a result of a breakage.
    It is possible that at least one fixed stop is provided in the gear arrangement 1 or a plurality of fixed stops are provided, although this is not absolutely necessary. With this fixed stop or these fixed stops can, if it comes to a demolition of the elastic element 5, the relative rotatability of the radially inner member 4 relative to the radially outer member 5 are limited, whereby the gear assembly 1 an additional reliability in an at least partial damage having elastic element 5. The gear arrangement 1 can therefore have a corresponding fail-safe mechanism both in the radial direction and in the circumferential direction 19.
    Although the use of the gear assembly 1 in a mass balance has been described above, this is not meant to be limiting, although this is the preferred application of the gear assembly 1. The gear arrangement 1 can therefore also be used in other assemblies, for example in a camshaft drive, a timing drive, a high-pressure pump, etc.
    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 construction of the gear arrangement 1, these or their components have been shown partially unevenly and / or enlarged and / or reduced in size.
    List of Reference Numerals 1 gear arrangement 31 cavity 2 mass balance 32 recess 3 component 33 imbalance mass 4 component 34 ring element 5 element 35 release 6 toothing 36 release 7 direction 37 projection 8 projection 38 base 9 distance 39 spring 10 bottom 40 receptacle 11 end wall 41 receptacle 12 surface 42 top 13th Surface 43 Offset 14 End wall 44 Ring element 15 Fleas 16 Width 17 Gap 18 Projection 19 Circumferential direction 20 Base 21 Width 22 Deformation element 23 Height 24 Bottom 25 Bottom 26 Unbalance element 27 Recess 28 Hub part 29 Ring land 30 End face
    权利要求:
    Claims (11)
    [1]
    1. gear arrangement (1) with a first component (3) and a second component (4), wherein the first component (3) has a toothing (6), the second component (4) at least partially within the first component (3 ), and wherein between the first component (3) and the second component (4) at least one elastically deformable element (5) is arranged, characterized in that the at least one elastically deformable element (5) of an elastic deformation in the circumferential direction ( 19) opposes a different resistance than in the radial direction.
    [2]
    2. Gear arrangement (1) according to claim 1, characterized in that the elastically deformable element (5) opposite to an elastic deformation in the circumferential direction (19) and in a clockwise direction opposite to an elastic deformation in the circumferential direction (19) and against the clockwise.
    [3]
    3. gear arrangement (1) according to claim 1 or 2, characterized in that the first component (3) below the toothing (6) in the axial direction (7) projecting first projections (8), between which gaps (17) are formed in that further the second component (4) has in the axial direction (7) projecting second projections (18) which engage in the gaps (17) between the first projections (8) of the first component (3) and that the at least one elastic deformable element (5) at least partially between the first projections (8) of the first component (3) and the second projections (18) of the second component (4) engages and in the region of the engagement exemptions (35).
    [4]
    4. gear arrangement (1) according to claim 3, characterized in that the exemptions (35) are formed as openings.
    [5]
    5. gear arrangement (1) according to one of claims 1 to 4, characterized in that the first component (3) and / or the second component (4) in the region of the system of at least one elastically deformable element (5) exemptions (36) have or have.
    [6]
    6. gear arrangement (1) according to one of claims 1 to 5, characterized in that the at least one elastically deformable element (5) as an elastomeric ring with deformation elements (22) is formed.
    [7]
    7. gear arrangement (1) according to claim 6, characterized in that the elastomeric ring consists of a single elastomer.
    [8]
    8. gear arrangement (1) according to claim 1 to 7, characterized in that a plurality of elastically deformable elements (5) are arranged, which are formed as plate-shaped springs (39), wherein the springs (39) are oriented in the radial direction.
    [9]
    9. gear arrangement (1) according to claim 8, characterized in that the springs (39) engage in receptacles (40) in the first component (3) and in receptacles (41) in the second component (4).
    [10]
    10. gear arrangement (1) according to one of claims 1 to 9, characterized in that the resistance which opposes the at least one elastically deformable element (5) of an elastic deformation in the circumferential direction (19) is smaller than the resistance, the at least an elastically deformable element (5) opposes an elastic deformation in the radial direction.
    [11]
    11. gear arrangement (1) according to one of claims 1 to 10, characterized in that the second component (3) is guided with a front-side surface on the first component (3).
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    同族专利:
    公开号 | 公开日
    CN105626826B|2020-07-03|
    DE102015221812A1|2016-05-19|
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    US20160138696A1|2016-05-19|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50841/2014A|AT516397B1|2014-11-19|2014-11-19|gearing|ATA50841/2014A| AT516397B1|2014-11-19|2014-11-19|gearing|
    US14/926,631| US20160138696A1|2014-11-19|2015-10-29|Gearwheel arrangement|
    DE102015221812.0A| DE102015221812A1|2014-11-19|2015-11-06|gearing|
    CN201510799420.5A| CN105626826B|2014-11-19|2015-11-19|Gear device|
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