• 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 (1) comprising a first, radially inner Rin gelement (2) having a first ring element axis (9) in the axial direction, a two TES, radially outer ring member (3) with a second ring element axis (8) in the axial direction and a connecting element (4), wherein the second ring element (3) has a toothing (6) with teeth (7) rotatable about an axis of rotation, wherein furthermore the connecting element (3) extends in the radial direction between the first ring element (2) and the second ring element (3) is arranged and connected to these, and wherein the connecting element (4) consists at least partially of a rubber-elastic material. The first ring element axis (9) extends in the axial direction of the first, radially inner ring element (2) or the axis of rotation of the toothing (6) extends radially offset from the two th ring element axis (8) in the axial direction of the second, radially outer Rin gelementes ( 3) and / or the toothing (6) is formed with non-uniform teeth (7).
    公开号:AT514570A4
    申请号:T50107/2014
    申请日:2014-02-13
    公开日:2015-02-15
    发明作者:
    申请人:Miba Sinter Austria Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a gear comprising a first, radially inner Ringele¬ment with a first ring element axis in the axial direction, a second, radially outer ring member having a second ring member axis in the axial direction and a connecting element, wherein the second, radially outer ring member rotatable about a rotation axis toothing with teeth, wherein further the connecting element is arranged in the radial direction between the first, radially inner ring element and the second, radially outer ring element and is connected to the first, radially inner ring element and the second, radially outer Rin¬gelement, and wherein the connecting element at least partially a rubber-elastic material.
    To compensate for the backlash, known from the prior art gears, which are divided in the axial direction. Such a gear arrangement is known, for example, from the applicant's WO 2005/090830 A1, which discloses a gear for a backlash-free spur gear with a hub, with a sprocket carried by the hub, along an axis normal Teilungs¬ebene in two sub-rings, namely in a hub-fixed collar part And in a die¬¬ against coaxially rotatably mounted ring ring, is divided, and with a hub enclosing annular spring, which is supported with their mutually circumferentially opposite ends on one piece with the two sub-rings trained, overlapping each other in the axial direction supporting webs, in Umfangfangrichtung of the ring gear are arranged one behind the other.
    On the other hand, in the radial direction divided gears for vibration and noise insulation of machine components are known from the prior art. Thus, e.g. DE 71 35 220 U1 a vibration damped
    Transmission gear with an inner part, which has a ring groove on its outer circumferential surface, an annular, concentric and spaced from the inner part outer part, which also has a annular groove on its inner circumferential surface, which forms together with the arranged on the inner part annular groove a ring space, in which an inner and Externally non-rotatably connecting rubber-elastic profile ring is used, the undeformed radial extent is greater than that of the annular space formed between the inner and outer part, wherein at least one of the two annular grooves preferably in regular pitch has arranged extensions. Similar gears describe the US 2,307,129 A, US 4,674,351 A, EP2 623 820 A, DE 31 53 109 C2, DE 602 05 710 T2.
    However, it is also known that such radially divided gears are installed in an axially divided gear for play clearance.
    Thus, e.g. DE 10 2011 120 676 A1 discloses a toothed wheel with an inner ring element and an outer ring element, wherein a toothing is formed on the outer circumference of the outer ring element, wherein the inner ring element and the outer ring element are connected to one another via a vulcanized elastomer section. in that the ring elements are elastically movable relative to one another in the radial direction. This gear is placed on the hub of another gear, as described above. Similar gear arrangements are also described in DE 10 2011 120 266 A1 and DE 10 2009 015 958 A1.
    The present invention is based on the object to provide a way to play-release of two meshing gears.
    This object is achieved in the gear mentioned above in that the first ring element axis in the axial direction of the first, radially inner Rin¬gelementes or the axis of rotation of the toothing in the radial direction offset to the second ring element axis in the axial direction of the second, radially outer
    Ring element runs and / or that the toothing is formed with non-uniform Zäh¬nen.
    The advantage here is that a division of the gear in the axial direction no longer required, whereby the structure with respect to backlash Zahnradpaarun¬gen simplified. But this also simplifies the assembly of the gear pairing, since the ring gear is normally pre-tensioned in axially divided gears and secured in this position. After installation, the Posi¬ tion safeguard is then pulled out, whereby the teeth of the divided gear play engages freely in the toothing of the second gear. Such a securing element as well as the preload at the manufacturer of the gear are not required for the gear according to the invention. By dividing in the axial direction of the formation of the gear wheel, it is also possible to bring the entire Verzah¬nungsbreite of the gear with the toothing of the further gear in Ein¬griff. It is thus possible to reduce the axial width of the toothed wheel, as a result of which the axial installation depth can be reduced. In addition, the gear may also provide a low weight gear pair as compared to a prior art gear pair and functionality.
    The non-uniform toothing can be embodied in the form of a toothing which is designed eccentrically to the first annular axis in the axial direction of the first, radially inner annular element. This has the advantage that the connecting element can be made with a constant thickness in the radial direction, whereby fewer vibrations are generated in the gear. Thus, the noise of the gear during the meshing engagement of the spline with the teeth of the further gear can be reduced, so that the overall gear pair becomes quieter in operation. However, it is also possible to reduce the load on the connection areas between the two ring segments and the connection element.
    To avoid the eccentric arrangement of the second, radially outer Rin¬gelementes to the first radially inner ring member may be provided according to other Ausfüh¬rungsvarianten the gear that the teeth are formed with a different tooth thickness in the circumferential direction and / or that the teeth with a Flank crowning are provided, wherein the flank crowns of the teeth are different and / or that the gear pitch varies over the circumference of the toothing. It can thus be achieved the advantages mentioned for the eccentric formation of the dentation. Another advantage is that these geometric configurations of the teeth are relatively easy representable.
    It can be further provided in the gear that a wall thickness inradialer direction between the radially innermost edge and the Fußkreis the Ver¬zahnung the second, radially outer ring element is at least as large as half the tooth height of the teeth of the toothing. Thus, the mechanical loading of the connecting element can be reduced by the more uniform distribution of the load in the second, outer ring element, in particular in the embodiment of the toothed wheel with the second, radially outer ring element eccentric with respect to the first radially inner ring element.
    According to another embodiment of the gear can be provided that edges of the first, radially inner ring member in the connecting region between the first, radially inner cattle element and the connecting element and edges in the connecting region between the second, radially outer Rin¬gelement and the connecting element are provided with a rounding. The advantage here is that it can be used to improve the endurance of the toothed wheel, in particular of the connecting element. Due to the formation of round edges on the radially inner and the radially outer ring element, the punctual overloading of the connection region at the edges can be avoided and thus the tearing off of the connecting element can be better prevented. Thus, the occurring, constantly changing pressure and Zugdruckungen of the connecting element can be better absorbed by this addition, but also the notch effect of the edges can be avoided. It is thus possible to make the connecting element with respect to its Geo¬metrie simple. As a result of the rounding, the areas which are available for the connection of the radially inner ring element and the radially outer ring element with the connecting element are further increased, whereby the permanent load capacity can likewise be improved. Due to the roundness of the edges, it is also achieved that, when the connecting element is flush with the axial end faces of the two ring elements, the connecting element radially surrounds the ring elements in the connecting region, whereby tensile and compressive loads of the toothed wheel in the axial direction are likewise better absorbed can. As a side effect, the rounded edges have the advantage that the two ring elements can be better removed from the mold, if they are made of sintered materials.
    Furthermore, it can be provided that the connecting element projects in the axial direction over the first, radially inner ring element and the second, radially outer ring element, partially overlapping the first, radially inner ring element and / or the second, radially outer ring element, in the radial direction It is thus achieved a further improvement of the composite of Verbindungselemen¬tes with the two ring elements, which subsequently the Dauer¬festigkeit this compound can be improved.
    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 the gear in Explosionsdarstel¬lung.
    Fig. 2 shows the gear of Figure 1 in view of an axial end surface.
    Fig. 3 shows a variant of the gear in view of an axial end face;
    4 shows a section of the second, radially outer ring element of an embodiment variant of the toothed wheel in view of an axial end face;
    5 shows a tooth of the toothing of the second, radially outer Ringelemen-tes a variant of the gear in an oblique view.
    6 is a side view of a detail of another embodiment variant of the gear wheel;
    Fig. 7 is a play-free gear pair with a gear according to the invention, which is in meshing engagement with another gear.
    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 designations, wherein the disclosures contained in the entire description apply mutatis mutandis to the same parts with the same reference numerals. same component names can be transferred. Also, the location information chosen in the description, such as up, down, laterally, etc. related to the directly described and illustrated figure and these conditions are to be transferred in a change in position mutatis mutandis to the new situation.
    In FIGS. 1 and 2, a first embodiment of a gear 1 is darge¬stellt. The gear wheel 1 consists of or comprises a first, radially inner ring element 2, a / a second, radially outer ring element 3 and a / a connection element 4. The first, radially inner ring element 2 can also be Naben part and the second, radially outer Ring element 3 are referred to as sprocket.
    The first, radially inner annular element 2 and / or the second, radially outer annular element 3 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 radially inner ring element 2 and / or the radially outer ring element 3, wherein the radially inner ring element 2 and / or the radially outer ring element 3 can also consist of at least two different metallic materials.
    The connecting element 4 consists at least partially of a rubber-elastic material, for example of an (X) NBR ((carboxylated) acrylonitrile-butadiene rubber), HNBR (hydrogenated nitrile rubber), a silicone rubber (VMQ), NR (natural rubber ), EPDM (ethylene-propylene-diene rubber), CR (chloroprene rubber), SBR (styrene-butadiene rubber), etc., in which case material mixtures can be used in turn.
    By "at least partially" it is meant that in the connecting element 4, for example, stiffening elements, such as e.g. Fibers and / or threads, for example of metal, plastic, natural fibers, etc., or rods, etc. may be incorporated. Preferably, however, the connecting element 4 consists exclusively of a rubber-elastic material.
    The first, radially inner ring element 2 has an axially extending recess 5, in particular a bore. As a result, the first, radially inner ring element 2 can be arranged on a shaft, not shown.
    The second, radially outer ring element 3 has a toothing 6 with teeth 7 on the radially outer end face. This toothing 6 may have a form adapted to the particular application of the toothed wheel 1, for example for the formation of a toothed gear wheel. Furthermore, the toothing 6 can extend in the axial direction of the toothed wheel 1 over the entire width of the second, outer ring element 3 or only over a partial region of this width.
    The second, radially outer ring element 3 is arranged in the radial direction above the first, radially inner ring element 2.
    Between the first, radially inner ring member 2 and the second, radially äuße¬ren ring member 3, the connecting element 4 is arranged. With this connecting element 4, the first, radially inner ring element 2 and the second, radially outer ring element 3 are connected to one another to form the gearwheel 1.
    As can be seen better from FIG. 2, a ring element axis 8 in the axial direction of the radially second ring element 3 (indicated by a cross in FIG. 2) is offset in the radial direction relative to a ring element axis 9 in the axial direction of the radially first ring element 2 (indicated in Fig. 2 with a cross). In other words, the second, radially outer ring member 3 eccentric, that is not coaxial, angeord¬net to the first, radially inner ring member 2.
    In order to form the eccentricity, an outer circumference 10 of the first, radially inner ring element 2 can deviate correspondingly from the circular geometry, for example with a one-sided bulge in the radial direction (that is, approximately cam-shaped).
    The eccentricity can also be generated with the aid of the Ver¬ binding element 4 in this embodiment. This is primarily because the connecting element 4 is preferably produced by vulcanization, in particular hot vulcanization, onto the first, radially inner ring element 2 and the second, radially outer ring element 4. The eccentricity can thus be generated by positioning the second, radially outer ring element 3 with an offset of its annular segment axis 8 to the ring element axis 9 of the first, radially inner ring element 2, and then introducing a rubber compound into the gap between the two ring elements 2, 3 vulcanized. This has the advantage that the two ring elements 2, 3 ausgebil¬det with an annular geometry and thus can be made easier.
    A radial distance 11 of the first ring element axis 9 from the second ring segment axis 8 can be selected from a range of 0.01 mm and 1 mm.
    The tooth thickness in the sense of the invention and the technical usage is defined as the width of the tooth at the level of the pitch circle, the pitch circle being the circle with the diameter at which the values for the thickness of the teeth and the width of the gaps of a toothing are equal are big.
    According to one embodiment of the gear 1 according to FIGS. 1 and 2, it may also be provided that the first, radially inner ring element 2 and the second, radially outer ring element 3 are arranged concentrically with respect to one another so that the two ring element axes 8, 9 coincide. In order to achieve an eccentricity in this embodiment variant, it can be provided that only the toothing 6 is formed eccentrically to the two ring element axes 8, 9. Thus, an axis of rotation of the toothing 6 around which the teeth 7 rotate during the rotation of the toothed wheel 1, unlike the ring element axes 8, 9, i. this axis of rotation is radially offset from the axially extending ring element axes 8, 9 offset. The Rotati¬onsachse can also be offset by the distance 11, as already stated above, in the radial direction relative to the ring element axes 8, 9, so in this case the cross, in Fig. 2, the Ringelementach¬se 9 of the second, radially outer ring member 3 represents, in the gegenständli¬chen embodiment, the axis of rotation of the toothing 6 represents.
    In other words, the axis of rotation of the gear 1 per se, which is identical to the ring element axis 8, and the axis in the axial direction by the center of gravity of the gear 1 do not coincide, but this center of gravity is the distance 11 in the radial direction relative to the Rin¬gelementachse 8 offset.
    This embodiment variant of the toothed wheel 1 can be produced, for example, in such a way that, in a first step, the two ring elements 2, 3 are arranged coaxially with one another and connected to the connecting element 4, and that in a further step the toothing 6 is ground eccentrically to the ring center axis 8 becomes.
    In the following Figures 3 to 6 are each further and possibly selbsteigenständige embodiments of the gear 1 shown (partially only sections of the gear 1 are shown), again for the same part reference numerals or component designations as in the vorherigesFig. 1 and 2 are used. In order to avoid unnecessary repetition, reference is made to the detailed description of the preceding FIGS. 1 and 2.
    Alternatively or in addition to the variant of the gear 1 described above, there is also the possibility that the toothing 6 is formed with non-uniform teeth 7.
    For this purpose, it can be provided according to a first embodiment of the non-uniformly ausgebil¬deten teeth 7, that the toothing 6 is formed eccentrically to the first ring element axis 9 in the axial direction of the first, radially inner ring element 2.
    For the preparation of the eccentric toothing 6, the teeth can be machined 7spanend, in particular be ground eccentrically. In this case, preferably only one tooth flank 13 or both tooth flanks 13, 14 of the teeth 7 are ground. Tooth heads 15 and / or tooth gaps 16 are preferably not processed, but it is also possible to machine the tooth tips 15 and / or the Zahn¬ flanks 16, in particular to grind.
    Since the eccentric grinding of gears is known per se from the prior art, it is dispensed with further explanations thereto and is verwicht to the relevant state of the art for grinding gears.
    To grind the toothing, the second ring element axis 8 is fixed in the axial direction of the second, radially outer ring element 3 out of the concentricity to the first ring element axis 9 in the radial direction (as indicated in FIG. 3) in a grinding machine. Thus, a pitch circle 17 of the toothing (the definition of the pitch circle 17 is reproduced above) runs eccentrically in the finished toothed wheel 1, i. not coaxial with the periphery 10 of the first radially inner ring element 2.
    The radial distance 11 between the first ring element axis 9 in the axial direction of the first, radially inner ring element 2 and the center of Teilkrei¬ses 17 can be selected for the grinding of the toothing 6 from the above-mentioned range for the distance 11.
    The second, radially outer ring element 3 is then arranged in the gear 1 in the following so that the gear is aligned to the unbalance center of gravity ± 3 teeth 7.
    Instead of grinding, any other suitable type of material removal machining of the toothing 6 may be used.
    Preferably, the toothing 6 is formed by a value eccentric to the first Rin¬gelementachse 9 in the axial direction of the first radially inner ring member 2, which is selected from a range of 0.01 mm to 1 mm, bezo¬gen on the axis of rotation of the gear. 1 ,
    Alternatively or in addition to the above-described Ausführungsvarian¬ten the gear 1 may be provided to form the non-uniform teeth 7 of the serration 6 that the teeth 7 are formed with a different Zahndi¬cke 18 in the circumferential direction, as shown in fragmentary manner in FIG. 4, which shows a section of the second, radially outer ring element 3, is shown.
    The tooth thickness 18 of the individual teeth 7 can be changed by a value selected from a range of 10% to 100% of the tooth thickness 18 of the tooth 7 with the smallest tooth thickness 18.
    It is possible that the toothing 6 has a sequence of thicker and thinner teeth 7, wherein a thinner tooth 7 is followed by a thicker tooth 7. The toothing 6 in this case can only have teeth with two different tooth thicknesses 18.
    But it is also possible to form the teeth 7 of the toothing with several unterschied¬liche tooth thicknesses 18, for example, three, four, five, six, etc., so that so that a greater variance of the tooth thicknesses 18 is introduced into the toothing 6 , The arrangement may, for example, be such that two or more thinner teeth 7 are arranged next to each other, and subsequently a thicker tooth 7 or a plurality of thicker teeth 7 are arranged, as shown by way of example in FIG.
    It can further be provided that the tooth thickness 18 of the teeth 7 continuously increases in the circumferential direction over the region of a circle segment and again continuously decreases over a further region of an adjoining circle segment, whereby also several regions with continuous increase and subsequent continuous decrease of the tooth thickness 18 can be arranged in Um¬fangsrichtung one behind the other. For example, two or three or four or five regions may each be arranged with a continuous increase in the tooth thickness 18, each circumferentially separated from a region with a continuous decrease in tooth thickness 18. The tooth thickness 18 can be increased maximally by a value that is selected from a range of 5% of the tooth thickness 18 of the thinnest tooth 7 to 100% of the tooth thickness 18 of the thinnest tooth 7. The same applies to the reduction of the tooth thickness 18.
    According to a further embodiment variant of the toothed wheel 1, it can be provided that the teeth are provided with a flank crown, wherein the flank crowning of the teeth is different. For this purpose, a tooth 7 with a flattening crown is shown in FIG. 5. The different flank crowns may be designed such that a radius of the flank crown is varied.
    With regard to the sequence of teeth 7 with different flank crowning, reference is made to the above statements regarding the varying tooth thickness 18, which can be applied accordingly.
    In addition, it may be provided, as shown in FIG. 5, that the flank crown of at least one tooth flank 13 is asymmetrically formed within a tooth 7 such that, for example, a recessed portion 20 of the flattening crown extends in a direction which is at an angle to the axial direction of the flank Gear 1 runs.
    According to another embodiment of the gear 1 can be provided that the gear pitch varies over the circumference of the toothing.
    The gear pitch designates a distance 22 from a tooth 7 to the next at the level of the pitch circle 17th
    This embodiment is also shown in Fig. 4.
    It should be noted at this point that in the formation of the teeth 7 with unter¬schiedlicher tooth thickness 18, the gear pitch, so the distance 22 between the teeth 7, can also be the same size.
    Due to the eccentric machining of the toothing 6, a wall thickness 24 in the radial direction between a radially innermost edge 25 (FIG. 4) and a root circle 26 of the toothing 6 of the second, radially outer edge element 3 can also be reduced. In this case, it is preferred if the wall thickness 24 in the radial direction between the radially innermost edge 25 and the root circle 26 of the toothing 6 of the second, radially outer ring element 3 is at least half of a tooth height 27 in the radial direction of the teeth 7 of the toothing 6. In particular, this wall thickness 24 be selected from a range of 50% of the tooth height 27 to 150% of the tooth height 27.
    As shown in FIG. 6, according to a further embodiment variant of the toothed wheel 1 it can be provided that axially outer edges 28, 29, i. the edges 28, 29 in the transition region from a radially outer end surface 30 to axial Endflä¬ 31, 32, the first, radially inner ring member 2 and axially outer edges 33, 34, i. the edges 33, 34 in the transition region from a radially inner end face 35 to axial end faces 36, 37 of the second, radially outer Ringelemen¬tes 3 are executed rounded, so are provided with a rounding.
    The radius of the curves is preferably selected from a range of 0.1 mm to 2 mm, in particular from a range of 0.4 mm to 1.5 mm.
    It is possible that the radius of all curves is the same size. But it is also possible that at least one of the curves has a radius different from the rest of the curves. For example, the two curves of the first, radially inner ring element 2 can have a larger radius than the two curves of the second, radially outer ring element 3. However, it is also possible that the curves in the region of one axial side of the gear 1, e.g. in the region of the axial end faces 31, 36, have a larger radius, that is to say the curves of the second axial side of the toothed wheel 1, that is to say in the region of the axial end faces 32, 37. With these variants of the toothed wheel 1, i. the different design of the curves, the most different load cases of the gear 1 in the axial and radial direction can be considered better.
    In the simplest case, the curves 21 to 24 are designed as pitch circles, for example four-circle circles. But there are also other versions of Rundun¬gen possible.
    As can be seen from FIG. 6, the connecting element 4 can protrude in the axial direction via the first, radially inner ring element 2 and the second, radially outer ring element 3 and in the radial direction the first, radially inner ring element 2 and / or the second, radially outer ring element 3 partially overlapping. The connecting element 4 can therefore in particular have an at least approximately H-shaped or an H-shaped cross-section.
    But it is also possible that the connecting element 4 is flush with the axial end surfaces 31,32 of the first radially inner ring member 2 and / or flush with the axial end surfaces 36, 37 of the second, radially outer Rin¬gelementes 3 is formed.
    It can further be provided that the first, radially inner ring element 2 and / or the second radially, outer ring element 3 on at least one of the axial end faces 31, 32 or 36, 37, preferably in all end faces 31, 32, 36, 37, at least one Groove, in particular an annular groove, has or have and that the connecting element 4 extends into this groove (s).
    Alternatively or additionally, it may be provided that the first, radially inne¬ ring element 2 in the end face 30 and / or the second radially outer Rin¬gelement 3 in the end face 35 at least one groove, in particular an annular groove comprises or have and that the connecting element 4 extends into this groove (s).
    It is also possible for a plurality of grooves to be arranged next to each other, so that the end face 30 and / or the end face 35 and / or at least one of the end faces 31, 32 or 36, 37 is designed in the manner of a toothing in this area or these areas. are.
    There is also the possibility that, instead of grooves, at least one projection on the end face 30 and / or the end face 35 and / or at least one of the end faces 31, 32 or 36, 37 is or are formed in this area or areas in this way ,
    Furthermore, there is the possibility of a mixed embodiment, that therefore at least one projection is formed on the end face 30 of the first, inner ring element 2 and at least one projection on the end face 35 of the second, outer ring element 3 which projects in the direction of the end face 30 over the Front surface 35 protrudes. All edges in the region of the groove (s) may also be rounded with a view to the above-mentioned reasons.
    To produce the gear 1, the connecting element 4 can be preformed and then connected to the first, radially inner ring element 2 and the second, radially outer ring element 3, for example exclusively due to static friction or by the use of an adhesive, such as , an adhesive.
    In the preferred embodiment of the gear 1, however, the connecting element 4 is vulcanized onto the radially inner ring element 2 and the radially outer ring element 3 in a corresponding shape, in particular vulcanized hot. For the improvement of the connection formation, there is also the possibility that the at least individual surfaces, in particular all surfaces, are roughened at least in the region of the connection to the connecting element 4, for example by (sand) blasting or by grinding, etc.
    It is also advantageous, however, if open-pore sintered components for the first, radially inner ring element 2 and / or the second, radially outer ring element 3 are used at least in the connecting regions, since this likewise forms a type of wedging between the connecting element 4 and the first, radially inner ring element 2 and / or the second, radially outer ring element 3 can be achieved.
    It may also be advantageous if at least the surfaces of the first, radially inner ring element 2 and / or the second, radially outer ring element 3 are subjected to plasma pretreatment or plasma activation in the region of the connection to the connecting element 4.
    For the sake of completeness, a backlash-free gear pairing 38 is shown in FIG. 7. This comprises the gear wheel 1 according to the invention and a further gearwheel 39. The toothing 6 of the gearwheel 1 is in engagement with a toothing 40 of the further gear 39 in order to transmit one torque .Dabei either the gear 1 or the further gear 39 can be driven and driven the gear 1 from the other gear or the other gear 39 driven by the gear 1.
    The embodiments show possible embodiments of the Zahnrades1, which should be noted at this point that also various combinations of Einz¬ individual variants are possible with each other.
    For the sake of order, it should finally be pointed out that in order to better understand the construction of the toothed wheel 1, this or its constituent parts have been shown in part to be out of scale and / or enlarged and / or reduced in size.
    REFERENCE SIGNS 1 gear 31 end face 2 ring member 32 end face 3 ring member 33 edge 4 connecting element 34 edge 5 recess 35 end face 6 tooth 36 end face 7 tooth 37 end face 8 ring element axis 38 gear pair 9 ring element axis 39 gear 10 circumference 40 toothing 11 distance 12 diameter 13 tooth flank 14 tooth flank 15th Tooth head 16 Tooth gap 17 Partial circle 18 Tooth thickness 19 Radius 20 Area 21 Direction 22 Distance 23 Tooth circle 24 Wall thickness 25 Edge 26 Foot circle 27 Tooth height 28 Edge 29 Edge 30 Face
    权利要求:
    Claims (8)
    [1]
    A gear (1) comprising a first, radially inner ring element (2) having a first ring element axis (9) in the axial direction, a second, radially outer ring element (3) having a second ring element axis (8) in the axial direction and a connecting element (4) , wherein the second, radially outer ring element (2) has a toothing (6) with teeth (7) rotatable about a rotation axis, wherein the connecting element (3) also extends in the radial direction between the first, radially inner ring element (3). 2) and the second, radially outer ring element (3) is arranged and with the first, radially inner ring member (2) and the second, radially outer ring member (3) is connected, and wherein the Verbin¬ element (4) at least partially from a be¬steht elastomeric material, characterized in that the first ring element axis (9) in the axial direction of the first radially inner ring member (2) or the axis of rotation of the toothing (6) in the radial direction offset from the second ring element axis (8) in the axial direction of the second, radially outer ring element (3) runs and / or that the toothing (6) with non-uniform teeth (7) is formed.
    [2]
    2. gear (1) according to claim 1, characterized in that the Ver¬zahnung (6) eccentrically to the first ring element axis (9) in the axial direction of the first, radially inner ring element (2) is formed.
    [3]
    3. gear (1) according to claim 1 or 2, characterized in that the teeth (7) are formed with a different tooth thickness (18) in the circumferential direction.
    [4]
    4. gear (1) according to one of claims 1 to 3, characterized gekennzeich¬net that the teeth (7) are provided with a Flankenballigkeit, wherein the Flan¬kenballigkeiten the teeth (7) are different.
    [5]
    5. Gear (1) according to one of claims 1 to 4, characterized gekennzeich¬net that the gear pitch varies over the circumference of the toothing (6).
    [6]
    6. gear (1) according to one of claims 1 to 5, characterized gekennzeich¬net that a wall thickness (24) in the radial direction between the radially innermost edge (25) and a root circle (26) of the toothing (6) of the second, radially outer ring element (3) is at least as large as half a tooth height (27) of the teeth (7) of the toothing (6).
    [7]
    7. Gear (1) according to one of claims 1 to 6, characterized gekennzeich¬net that edges (28, 29) of the first, radially inner ring element (2) in Verbin¬dungsbereich between the first, radially inner cattle element (2) and the Ver¬ binding element (4) and edges (33, 34) in the connecting region between the second, radially outer ring member (3) and the connecting element (4) are provided with ei¬ner rounding.
    [8]
    8. gear (1) according to one of claims 1 to 7, characterized gekennzeich¬net that the connecting element (4) in the axial direction over the first, ra¬dial inner ring element (2) and the second, radially outer ring element (3) vorste¬hend and in the radial direction, the first, radially inner ring member (2) and / or the second, radially outer ring member (3) partially overlapping extends.
    类似技术:
    公开号 | 公开日 | 专利标题
    AT514570B1|2015-02-15|gear
    AT514590B1|2015-02-15|gear
    AT517484B1|2017-02-15|gearing
    AT516397B1|2016-05-15|gearing
    DE102014104284A1|2015-10-01|GEAR
    DE102012210465A1|2013-12-24|Planetary gear device i.e. wolfrom gear, for use as e.g. running gear in vehicle drive train, has gearing of planetary gears pressed against gearing of ring gears of internal gear by bias force in mounted condition of planetary gears
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    DE102019103112A1|2019-08-22|gear
    AT517424B1|2019-09-15|Device for releasing play of meshing gears of a gear drive
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    AT520015B1|2019-02-15|Assembly with a spline
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    DE102013017482A1|2015-04-23|Gear and method for producing a gear
    DE102019212220A1|2021-02-18|Strain wave gear
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    EP3346163A1|2018-07-11|Gear wheel and toothed wheel arrangement of a combustion engine
    AT522070B1|2020-08-15|gear
    AT521959B1|2020-07-15|gear
    AT520531B1|2019-05-15|gear
    DE102017202418B4|2018-10-11|gear unit
    DE102012219216A1|2014-04-24|Planetary bolt used for vehicle, has hollow-shaped inner surface, cylindrical outer surface and wall which are completely interrupted in circumferential direction by slot, where slot is extended between two axial ends of main portion
    DE102017217215A1|2019-03-28|Gear combination with fail-safe, in particular for use for driving an oil pump
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    同族专利:
    公开号 | 公开日
    AT514570B1|2015-02-15|
    CN104847868A|2015-08-19|
    CN104847868B|2019-01-22|
    DE102014225192A1|2015-08-13|
    US20150226303A1|2015-08-13|
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    FR2834029B1|2001-12-20|2004-02-27|Renault|BALANCING SYSTEM FOR A COMBUSTION ENGINE|
    AT413748B|2004-03-22|2006-05-15|Miba Sinter Austria Gmbh|GEAR FOR A GAME-FREE HEAD WHEEL STAGE|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50107/2014A|AT514570B1|2014-02-13|2014-02-13|gear|ATA50107/2014A| AT514570B1|2014-02-13|2014-02-13|gear|
    DE102014225192.3A| DE102014225192A1|2014-02-13|2014-12-09|gear|
    US14/616,391| US20150226303A1|2014-02-13|2015-02-06|Gear|
    CN201510075569.9A| CN104847868B|2014-02-13|2015-02-12|gear|
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