• 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:

    公开号:AT510283A4
    申请号:T0162510
    申请日:2010-09-29
    公开日:2012-03-15
    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 gear body on which in the axial direction above a hub on the one hand for receiving a shaft and on the other hand for arranging the rotatable gear is arranged thereon, for what the rotatable gear has a recess coaxial with an axially extending central axis of the main gear, and wherein the main gear is connected to the rotatable gear by means of a bayonet lock, and a method of manufacturing a bayonet lock for a main gear and a relatively circumferentially rotatable gear Gear arrangement, wherein the main gear has a gear body on which in the axial direction above a hub on the one hand for receiving a shaft and on the other hand to arrange the rotatable gear on it arrange et is what the rotatable gear has a coaxial with an axially extending central axis of the main gear recess.
    Such a gear arrangement is known for example from the applicant's WO 2005/090830 A1, which is a gear for a backlash-free spur gear with a hub, with a hub-supported ring gear, along an axis-normal parting plane in two sub-rings, namely in a hub-fixed ring part and in a coaxially rotatably mounted relative to this ring ring, divided, and with a hub enclosing annular spring, which is formed with their mutually circumferentially opposite ends formed integrally with the two sub-rings, overlapping each other in the axial direction supporting webs, the are arranged in the circumferential direction of the ring gear one behind the other. The support web of a sub-rim passes through the other sub-rim in a passage opening with clearance in the circumferential direction and forms the support web of the sub-rim with the passage opening a mounting stop limiting mounting stop for the other support web. The ring collar is secured axially on the hub, for example by means of a snap ring. N201W22500 * »· · · · ·
    -2-
    From WO 2008/142 * 131 A2, such a gear arrangement is also known, comprising two gears, one of which is rotatably disposed against the other within certain limits. The two gears are coupled together via a spring element. The spring element is made in one piece with one of the gears.
    In order to secure the axial position of the two gears to each other after adjusting the position of the teeth to each other, a bayonet closure may be arranged.
    It is the object of the present invention to improve an aforementioned gear arrangement with respect to the connection of the two gears with each other. It is a further object of the invention to provide an improved method of manufacturing the gear assembly.
    This object of the invention is achieved by the gear arrangement mentioned above, in which the bayonet lock between the hub and the rotatable gear and / or between the hub and a voltage applied to the rotatable gear spring element is formed.
    The object is further achieved by the method mentioned at the outset, comprising the steps: sintering of a one-piece preform for the main gear from the gear body and the hub, starting at the periphery of the hub from an end face of the hub, in the axial direction on the gear body extending recesses are formed, which extend to a, the end face of the hub in the axial direction opposite Ausnehmungsendwand, and each having two side walls and a bottom surface, wherein at least one of the side walls forms an angle to the bottom surface of the recess, which is greater than 90 is; - Machining the hub of the preform in the circumferential direction, whereby the Ausnehmungsendwände removed and partially undercuts are formed, whereby hub protrusions are formed, which form part of the bayonet closure.
    By the formation of the bayonet lock between the hub, which receives the shaft on which the gear arrangement is arranged, and the rotatable gear is achieved that, unlike the prior art, an additional hub on the main gear is not required, whereby the structure the gear assembly can be simplified and with respect to the distribution of forces between the main gear and the rotatable gear during operation of the gear assembly occurring forces can be improved. In addition, the assembly of the gear arrangement is simpler, since an additional axial securing for securing the relative position of the two gears in the axial direction to each other can optionally be dispensed with.
    The formation of the bayonet lock between the spring element and the hub also achieves an axial securing of the rotatable toothed wheel, i. that thus the relative position of the rotatable gear in the axial direction of the gear assembly can be fixed, with additional connecting elements for connecting the rotatable gear to the main gear are not required. Due to the arrangement of the bayonet closure in connection with this design of the bayonet closure, it is also possible, a larger contact surface between the closure elements of the bayonet closure, ie. between "finger elements" or to provide tongues of the spring element and the closure elements of the hub, whereby a lesser wear of the bayonet lock, in particular the spring element, or the entire gear arrangement is achieved. Due to geometrical conditions, due to the necessity of pushing and hooking the tongues of the spring element into the corresponding groove in the hub, according to the prior art, as e.g. is described in the applicant's AT 506 961 B1, currently only eight fingers can be formed, resulting in a correspondingly smaller contact surface results. By replacing the Einhängenut through the bayonet lock a larger number of finger elements can be arranged.
    Preferably, the main gear is produced by sintering. To form the closure elements, in particular the hub projections, as part of the bayonet closure so that a subsequent machining is required to form the "groove" between the closure elements and the gear body of the main gear. In preparation of the closure elements, the main gear is made on the hub with recesses in the region of the circumference of the hub, which form in the finished main gear, the gaps between the closure elements in the circumferential direction, which allow the passage of the corresponding projections on the rotatable gear to form the bayonet closure. During the subsequent machining, the machining tool thus partially encounters "free positions" in these areas (due to the removal of the recess end walls) so that the machining tool is immersed several times over the circumference of the hub into the material of the hub. Here, the inventive method has the advantage that by the N2010 / 22500
    Forming an obtuse angle between the side walls and the bottom surfaces of the recesses - viewed in the circumferential direction - better protection of the machining tool when re-immersion in the material is achieved, so that the tool life can be extended. In addition, this ensures that the formation of burrs in the area of the machining of the main gear is reduced.
    To form the bayonet lock, radially outwardly protruding hub projections can be arranged on the hub. It is thus a relatively simple production of the bayonet closure allows, which can be done in particular after a sintering process. These radially outwardly projecting hub projections can also be formed in terms of their cross-sectional area - viewed in the axial direction of the gear assembly - relatively large area, whereby a better wear behavior by the presence of a large contact surface of the closure elements of the bayonet catch of the rotatable gear on the closure elements of the bayonet lock of the main gear, i. the hub projections, can be achieved.
    According to one embodiment, it is provided that the hub projections are arranged symmetrically distributed over the circumference of the hub, so that the contact surfaces of the rotatable gear on the main gear are distributed uniformly over the circumference of the main gear, and thus distributes the forces acting uniformly over the entire circumference of the gear assembly can be. This positively influences the wear behavior.
    In the axial direction may be formed between the hub projections and the gear body extending in the direction of the circumference of the hub, undercut, whereby the sealing strength of the bayonet closure can be improved.
    Preferably, the undercut extends continuously over the circumference of the hub to facilitate the assembly of the gear assembly, since thus the rotatable gear on both sides of the hub projections can be pushed onto the hub.
    In view of reducing the wear of the gear assembly, it is advantageous if the hub projections in the circumferential direction of the hub have an overall length of between 20%, in particular 40%, preferably 50%, and 80%, in particular 60%, of the length of the circumference the hub is. N2010 / 22500 -5- * · · · * * · 4 »* • · 4« · 4 | 44 · ·· ** · «* * * 44 · t 4 44 444 · *
    Preferably, the hub projections viewed in the axial direction, ie in plan view of the plane surface, a trapezoidal cross-section. On the one hand so that the assembly of the gear arrangement is simplified. In particular, however, the manufacture of the bayonet closure is thereby improved by, as has already been explained above, thereby reducing the wear of the machining tools.
    It is also possible that are formed to form the bayonet catch in the recess of the rotatable gear and / or in a recess of the spring element radially inwardly projecting projections, since with this embodiment, the sinter-technical production of the rotatable gear can be simplified by the Press molds can be made simpler.
    Preferably, the spring element and / or the rotatable gear has an anti-rotation lock in order to at least approximately fix the relative position of these two elements of the gear arrangement relative to one another. By the term "at least approximately fixed" is meant that movements by a maximum of +/- Γ in the circumferential direction of the spring element are possible.
    This rotation can be formed by at least one tab which engages in a recess of the rotatable gear, or according to another variant by at least one projection on the spring element and / or be formed on the rotatable gear. It is thus an inexpensive and the assembly of the gear arrangement simplistic execution of rotation possible.
    To simplify the assembly of the gear arrangement can be provided that a transition between an end face of the hub and the peripheral surface in the hub projections is rounded or beveled, since thus the sliding of the rotatable gear can be simplified to the hub of the main gear.
    According to one embodiment variant of the method, it is provided that the angle between the at least one side surfaces and the bottom surfaces is selected from a range with a lower limit of 95 6, in particular 100 and an upper limit of 130 °, in particular 120 With regard to the tool protection and the processing speed In practice, angles from this angular range have proven to be particularly advantageous. N2010 / 22500 -6- * · * · «· 4
    • * * ψ «I I t · * · I · · · * * · ·
    It can also be provided that at least individual edges, preferably all edges, of the recesses are rounded or chamfered, whereby a further improvement with regard to the service life of the tool can be achieved, namely in the area of immersion of the tool in the material of Main gear of the angle in which the recessed surfaces are the tool is designed dull for this area, but at the same time this obtuse angle is limited only to the edge region, so that the removal rate of the material is not reduced. In addition, with this, i. due to the side surfaces of the recesses arranged at a smaller angle to the bottom surface compared to the edge region, the contact surface of the rotatable gear on the main gear in the assembled state of the gear arrangement is not reduced so much that the advantages of even loading of the bayonet closure over the circumference of the hub would be degraded ,
    Preferably, the rotatable gear is also produced by sintering, wherein radially inwardly extending projections are formed in the recess of the gear. It is thus possible without substantial finishing the production of the rotatable gear, with complex bayonet geometries are formed without the rotatable gear would have to be subjected to a machining reworking. For a better contact of the rotatable gear on the main gear can be provided that at an extending in the radial direction of the end face of the rotatable gear an annular web is formed.
    For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
    Each shows in a highly schematically simplified representation:
    Fig. 1 is a gear group according to the prior art in an exploded view;
    2 shows a first embodiment of a gear group according to the invention in an oblique view.
    Fig. 3 is a detail of the gear arrangement of Fig. 2;
    FIG. 4 shows a detail of the gear arrangement according to FIG. 2 cut in side view; FIG. N2010 / 22500 -7- • «« * ♦ · «* * *« «« »i
    Fig. 5, the rotatable gear of the embodiment of Figure 2 in an oblique view.
    6 shows a preform of the main gear of the embodiment of Figure 2 in an oblique view ..;
    FIG. 7 shows the main gear wheel according to FIG. 6 in an oblique view after a machining operation; FIG.
    8 shows a further embodiment variant of a gear group according to the invention in an oblique view;
    FIG. 9 shows a detail of the gear arrangement according to FIG. 8; FIG.
    Fig. 10 shows a detail of a variant of a bayonet closure in cross section.
    By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component names, wherein the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or component names. Also, the location information chosen in the description, such as top, bottom, side, etc. related to the immediately described and illustrated figure and are to be transferred to the new situation mutatis mutandis when a change in position.
    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 in this case so-called Ω - spring, as described in WO 2005/090830 A1, which is thus in this scope of basic structure of the gear assembly 1 to the content present N2010 / 22500 -8- 44 * | Ι · · • fl
    t · I II * · • · · · «* * * * 4 4 4 * 4 4 4 • · * · | l < «« Fl
    Spelling belongs. For the bias, as described above, a support web is formed, which forms an assembly stop for another support web. The Fe-dereiement 7 abuts on these supporting webs with its two open end portions.
    To bias the further rotatable gear 4 in an axial direction 8 against the main gear, another spring element 9, which in this embodiment, the form of a plate spring, in particular a slotted plate spring to be designated in the broadest sense, arranged. This further spring element 9 has an outer ring 10, from which obliquely pointing radially inwards a plurality of tongues 11, so-called spring tongues, protrude. These tongues 11 are received by a circumferential groove 12, which is formed in an end portion 13 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 7 show a first embodiment of the gear arrangement 1 according to the invention.
    From Fig. 2, in turn, the main gear 2 and the adjacent thereto rotatable gear 4 can be seen. The rotatable gear 4 is arranged on the hub 5. This variant of the gear arrangement has u.a. the advantage that the additional spring element 9 of the embodiment of FIG. 1 for axial securing of the rotatable gear 4 is not required.
    Although not shown, in this and in all other embodiments of the invention, the biasing force for the rotatable gear 4 in the circumferential direction 3 by the spring element 7, for example, the D - spring generated.
    For connection and axial securing of the rotatable gear 4 on the main gear 2, a bayonet 14 is arranged between the hub 5 of the main gear 2 and the rotatable gear 4. For this purpose, as can also be seen in detail from FIG. 3, the hub 5 projects radially outwards via projecting closure elements, which are referred to below as hub projections 15. The rotatable gear 4 also has projections 16 which, however, are arranged running radially inwards in a recess 17 (FIG. 5). The recess 17 is formed coaxially with the hub 5 and serves to be able to postpone the rotatable gear 4 to the hub 5 of the main gear 2. For this purpose, an inner diameter 18 between two opposing projections 16, as shown in Fig. 5, a size N2010 / 22500, which corresponds at least approximately to an outer diameter 19 of the hub in the region between recesses 20, wherein the recesses 20 in the circumferential direction third formed between two adjacent hub projections 15 on the hub,
    By "at least approximately" is meant in this context that the inner diameter 18 at least the outer diameter 19 corresponds in terms of its dimension, but preferably is slightly larger, so that the rotatable gear 4 can be easily pushed onto the hub 5.
    The recesses 20 between two hub projections 15 have a width 21 in the circumferential direction 3, which is at least as large as a width 22 (Fig. 5) of the projections 16 on the rotatable gear 4 in the same direction, so that the projections 16 in these recesses 20th can be inserted. Preferably, the width 21 is slightly greater than the width 22. It is further preferred if the recesses 20 in the axial direction of the gear arrangement 1 have a cross section which corresponds at least approximately to the cross section in the same direction of the projections 16 of the rotatable gear 4.
    Behind the hub projections 15, an undercut 23 in the form of a groove is formed in the axial direction of the gear arrangement 1, as can be seen in particular from FIG. 4. The hub projections 15 are thus spaced in the axial direction to an end face 24 (FIG. 7) of a gear body 25 of the main gear 2 - the main gear 2 consists of the gear body 25 and the hub 5 - arranged. A width 26 of the undercut 23 or the groove is preferably selected such that it has a size which corresponds at least approximately to a width 27 (FIG. 5) in the axial direction of the projections 16 of the rotatable gear 4, wherein at least approximately It is meant that the width 26 of the undercut 23 is selected so that the rotatable gear 4 can be rotated in the circumferential direction 3.
    In the preferred embodiment, an end face 28 (FIG. 3) of the gear hub body 25 facing coplanar with the direction of the hub bosses 15 is oriented coplanar with the direction of the gear hub body 25 of the main gear 2, so that the undercut 23 is oriented circumferentially 3 of the gear assembly has a rectangular or square cross-section. However, it is also possible for this end face 28 to be arranged at an oblique angle to the end face 24 of the gear body 25, so that the undercuts 23 narrow in the circumferential direction. N2010 / 22500
    -10-
    On the one hand so that a higher contact pressure of the rotatable gear 4 is achieved to the main gear 2 in a certain position, on the other hand, so that the rotatability of the rotatable gear 4 can be limited.
    The limitation of the rotatability of the rotatable gear 4 in the circumferential direction 3 of the gear assembly 1 can also be achieved so that the undercut 23 in the circumferential direction 3 is not continuous, so that the hub projections 15 are only partially spaced from the end face 24 of the gear body 25 of the main gear 2 , In the preferred embodiment, however, the undercut 23 in the circumferential direction 3 is designed to be continuous, so that an annular groove is created which is open in the axial direction to the front in the region of the recesses 20. In this case, a groove bottom 29 (FIG. 3) is preferably formed planar with a bottom surface 30 of the recesses 20. However, there is also the possibility that the groove bottom 29 is offset in the radial direction against this bottom surface, for example, is formed deeper, so as to form a "lubricant groove". However, the groove bottom 29 may be seen to be higher in the radial direction from the longitudinal center axis through the gear assembly 1 than the bottom surfaces 30 of the recesses 20, in which case the projections 16 of the rotatable gear 4 must be adjusted, i. a height 31 of the projections 16 in the radial direction is smaller than a height 32 of the hub projections 15, the difference resulting from the height difference in the radial direction between the groove bottom 29 and the bottom surface 30. For the assembly of the gear assembly 1, the rotatable gear 4 is placed on the hub 5, wherein the projections 16 of the rotatable gear 4 are positioned in the axial direction in alignment with the recesses 20 of the hub 5, then the rotatable gear 4 in the axial direction in the direction pushed onto the gear body 25 of the main gear 2 and when the projections 16 of the rotatable gear 4 in the axial direction behind the hub projections 15 are rotated in the circumferential direction 3 against the main gear, whereby on the projections 16 and the hub projections 15 of the bayonet lock 14 for axially securing the rotatable Gear 4 is made relative to the main gear 2. Optionally, the spring element 7 can be arranged between the rotatable gear 4 and the main gear 2. In order to secure the relative position in this delivery position, in which the teeth of the rotatable gear 4 are aligned at least approximately in the axial direction with the teeth of the main gear 2, a securing element 33 is pushed through the two gears, to which both the rotatable gear 4 and the Main gear 2 each N2010 / 22500 - 11 - * *
    Weil have a recess 34 and 35 in the form of a breakthrough. After installation of the gear arrangement 1, this securing element 33 is removed again.
    It should be noted at this point that, although in Figures 2 to 5 each six hub projections 15 and six projections 16 and correspondingly six recesses 20 are shown, within the scope of the invention, a different number of hub projections 15, projections 16 and recesses 20th may be provided, for example, three, four, five, seven, eight, etc., or selected from a range with a lower limit of three and an upper limit of 30, as in the following even closer to a variant of the gear arrangement 1 without the projections 16 will be explained.
    Preferably, the hub projections 15 of the main gear 2 and the projections 16 of the rotatable gear 4 are arranged symmetrically about the circumference of the hub 5 and the recess 17 of the rotatable gear 4, i. that between the distances between the hub projections 15 and projections 16 are each the same size, as shown in FIGS. 2 to 5.
    However, it is also possible to arrange these hub projections 15 in asymmetrical distribution, whereby the assembly of the rotatable gear 4 can be simplified on the main gear 2.
    It is advantageous, however, if the hub projections 15 in the direction of the circumference of the hub 5 have an overall length which is between 20%, in particular 40%, preferably 50%, and 80%, in particular 60%, of the length of the circumference of the hub 5 , In this case, the length of the circumference of the hub 5 in height of the bottom surface 30 of the recesses 20 - viewed in the radial direction - measured.
    According to a further embodiment, at least transitions 36 between an axially forwardly facing end face 37 of the hub projections 15 and a peripheral surface 38 in the radially upper region of the hub projections 15 are rounded or chamfered. In particular, however, all transitions between the axially outwardly facing end face of the hub 5 and the circumferential surface of the hub 5 can be rounded or beveled, ie also the transitions in the area of the bottom surfaces 30 of the recesses 20 (it should be noted that the hub projections 15 are preferably are integrally formed with the hub, so that the peripheral surfaces 38 of the hub projections 15 form part of the total circumference of the hub 5). N2010 / 22500
    The main gear 2 is preferably made in one piece by a sintering process, i. that the hub 5 and the gear body 25 do not consist of two separate parts. For this purpose, from a powder, in particular a steel powder, a preform 39, as shown in Fig. 6, for example, by the usual steps, such as powder mixing, powder pressing in a mold, sintering, optionally after recompression and / or calibration produced. Essentially, this preform 39 differs from the finished gear only in that the undercut 23 or the (ring) groove between the thus not yet finished hub projections 15 and the gear body 25 is not yet formed, as the comparison of FIG and Fig. 7 shows. This undercut 23 is produced by the sintering process in a cutting process step with a tool, such as a chisel or by milling. Since the preform already has the recesses 20 between the hub projections 15 still to be finished, and recess end walls 40 of the recesses 20 are removed during the machining, the tool partially re-dips into the material of the hub 5 several times during the entire machining process. Thus, a higher tool wear and an increased burr formation are connected by the interrupted cut in the processing zone. In order to provide an improvement or remedy with regard to these problems, at least those side walls 41 of the recesses 20, which are simultaneously the side walls 41 of the Nabevorsprünge 15, in the during machining the tool from the region of the recesses 20 Coming immersed in the material of the hub 5, at least partially aligned at an angle to the bottom surface 30 which is greater than 90 0. In other words, the hub projections 15 at least partially have a trapezoidal cross-section when viewed in the axial direction.
    By "at least partially trapezoidal" is meant that the cross section of the hub projections 15 can also be composed of several geometric shapes, for example, the cross section consists of a rectangle with attached trapezoid.
    In addition to the formation of the cross section at least partially in the form of a rectangular trapezoid further exists the preferred possibility that a second side wall 42 of the recesses 20 and the hub projections 15, which is formed in the circumferential direction on the first side wall 41 following, inclined to the bottom surface 30 is formed, with an angle greater than 90 °. Embodiments of the cross section which is symmetrical, that is to say the two at least partially inclined side surfaces 41, 42 close the same angle value with the bottom surface 30, are therefore particularly preferred, so that the cross section of the hub projections 15 at least partially in the axial direction , Preferably entirely an isosceles trapezoid.
    The angle which at least one of the side surfaces 41, 42 encloses with the bottom surface 30 is preferably selected from a range with a lower limit of 95, in particular 100 °, and an upper limit of 130 °, in particular 120 °.
    Preferably, it is further provided that at least individual, in particular all, edges or transitions in the region of the hub projections 15 in the circumferential direction 3, ie the transitions or edges between the bottom surface 30 and the side walls 41, 42 and / or between the side walls 41, 42nd and a top wall 43 are rounded or beveled.
    It is not necessary in the context of the invention that the projections 16 of the rotatable gear 4 have a cross section, which follow the contour of the recesses 30 of the hub 5, although this is the preferred embodiment of the gear assembly 1.
    According to a further embodiment of the gear arrangement 1 is provided, which is formed on an end face 44 of the rotatable gear 4, a ring land 45, via which the rotatable gear 2 rests against the gear body 25 of the main gear 2, as shown in Fig. 4. On the one hand so that the rotatability of the rotatable gear 4 is simplified by the lower contact surface of the rotatable gear 4 on the main gear 2, on the other hand can thus between the rotatable gear 4 and the main gear 2, a recess 46 in the form of an annular groove for receiving the spring element 7 between the rotatable gear 4 and the main gear 2 are created. This recess 46 can also be created at least partially by a corresponding indentation in the gear body 25 of the main gear 2.
    But this ring land 45 can also be arranged on the gear body 25 of the main gear 2, or there is the possibility that both the rotatable gear 4 and the main gear 2 have such a ring land 45.
    Furthermore, there is the possibility that in the region where the annular web 45 rests against the main gear 2, in the latter an annular groove for receiving the annular web 45 N2010 / 22500 • *
    * * »» * * * M «« · | 4 "II" - 14-order, so as to achieve better guidance of the rotatable gear 4 on the main gear 2 during rotation.
    It is also possible that the rotatable gear 4 is recessed in a region 47 of the abutment of the projections 16 on the hub projections 15, so that the projections 16 are not in one plane with a main body 48 of the rotatable gear 4 above the region 47, as is shown in Fig. 5, so as to improve the formation of the Banjonettverschlusses between the two gears.
    8 and 9 show a variant of the gear arrangement 1 in an oblique view or detail view with the main gear 2, the adjacent thereto rotatable gear 4 and the spring element 9, in particular a plate spring.
    The bayonet closure 14 is formed in this embodiment of the gear arrangement 1 between the hub 5 and serving as an axial securing spring element 9. For this purpose, the hub 5 in turn on the radially outwardly projecting hub projections 15. For the formation of the bayonet closure 14, the projections 16 are also provided, which are however arranged unlike the above embodiment on the spring element 9 and are arranged by a spring element body 49 projecting radially inwardly in a recess 50 of the spring element 9. The recess 50 is sized, i. its diameter, so dimensioned that the spring element 9 can be pushed onto the hub 5, to which the projections 16 on the spring element 9, as in the above embodiment, the projections 16 are pushed through the recesses 20 between the hub projections 15.
    In contrast to the above embodiment of the bayonet fitting 14, no annular groove for receiving the projections 16 of the spring element 9 is ausgeblldet behind the hub projections 15, but the top walls 43 and top surfaces are angled, so so - viewed in the circumferential direction 3 of the gear assembly 1 - the hub projections in Area of the cover walls 43 have an at least approximately triangular cross-section. In this case, an edge-like center elevation 51 is dimensioned such that a circle following the center elevations of all hub projections 15 has a diameter 52 which is greater than a smallest inner diameter of the spring element 9, which is defined by the end regions of the tongue-shaped projections 16 of the spring element 9. In the axial direction and in the direction of the main gear 2, the diameter defined by the hub projections 15 becomes smaller again - in comparison to the diameter N2010 / 22500 15 defined by the edge-shaped center elevations 51 - so that the projections 16 of the spring element act on the cover walls 43 Hub projections 15 can be pushed, as shown in Fig. 9 in detail.
    The center elevations 51 of the hub projections 15 do not necessarily have to be edged in the shape of a ridge. For example, these center elevations 51 can also be flattened, resulting in a step-shaped course in the area of the cover walls 43 with regard to the cross section of the hub projections 15. There is the possibility that the center elevations 15 extend to an outer end face 53 of the hub projections 15.
    Of course, however, there is also the possibility in this embodiment variant of the bayonet closure 14 of providing the undercut 23 described in FIGS. 2 to 7 for receiving the projections 16 of the spring element 9. However, the former embodiment offers the advantage of less expensive production of the hub projections 15, since these can already be finished in a sintering process or the subsequent material removal in the machining of the main gear 2, if this is required, compared to the production of an annular groove is lower ,
    These embodiments have the advantage that a spring element 9 can be used, that more than eight tongues (in this case, the projections 16), as has already been described above.
    Preferably, the spring element 9 is provided with an anti-rotation 54, which is designed in the illustrated embodiment as a tab which is bent in the direction of the rotatable gear 4 and is received in a recess 55 of the rotatable gear 4.
    But it is also possible to form the rotation by at least one projection on the spring element 9 and / or the rotatable gear 2, which engages in a corresponding recess of the other element, for example, in particular circular recesses 56 of the spring element 9, such as this is shown in Fig. 8.
    10 shows a variant of a bayonet closure 14. In contrast to the embodiments described above, the hub projections 15 and the projections 16 of the rotatable gear 4 (not shown) in cross-section - N2010 / 22500 -16- * · * ··· «« »« «* * * *« T «« * * · · »* * * * * ♦« «« «··· ·« · · ··· * · · · »MM« in the circumferential direction 3 (eg 8) - each provided with an undercut 57, 58, so that the hub projections 15 and the projections 16 of the rotatable gear 4 are made angular and angulations 59 of the projections 16 of the rotatable gear 4 below bends 60 of the hub projections 15 engage , The bends 59, 60 thereby run at least approximately in the axial direction of the gear arrangement 1.
    In the context of the invention, mixed variants of the embodiments shown are also possible, for example that a bayonet closure 14 is formed both between the rotatable gear 4 and the hub 5 and between the spring element 9 and the hub 5.
    For the sake of completeness, it should finally be pointed out that the main gear 2 and the rotatable gear 4 are preferably made of a sintered steel, the further spring element 9 consists of a spring steel.
    The embodiments show possible embodiments of the gear arrangement 1, wherein it should be noted at this point that the invention is not limited to the specially dargestell th variants thereof, but also various combinations of the individual embodiments are mutually possible and this variation possibility due to the teaching of technical Acting by objective invention in the skill of those working in this technical field is the expert.
    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.
    The individual embodiments shown in FIGS. 2 to 7, 8 and 9 and 10 can form the subject of independent solutions according to the invention. N20t 0/22500
    Reference Designation 1 Gear arrangement 2 Main gear 3 Circumferential direction 4 Gear wheel 5 Hub 6 Recess 7 Spring element 8 Direction 9 Spring element 10 Ring 11 Tongue 12 Groove 13 End region 14 Bayonet catch 15 Hub projection 16 Projection 17 Recess 18 Inner diameter 19 Outer diameter 20 Recess 21 Width 22 Width 23 Undercut 24 End surface 25 Gear body 26 width 27 width 28 end face 29 groove bottom 30 bottom surface 31 height 32 height 33 securing element 34 recess 35 recess 36 transition 37 end face 38 peripheral surface 39 preform 40 Ausnehmungsendwand 41 side wall 42 side wall 43 top wall 44 end face 45 ring land 46 recess 47 area 48 main body 49 spring element body 50th Recess 51 center elevation 52 diameter 53 end face 54 anti-rotation 55 recess 56 recess 57 undercut 58 undercut 59 angling 60 bend N 2010/22500
    权利要求:
    Claims (17)
    [1]
    -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 gear body (25) on which protrudes in the axial direction a hub (5) on the one hand for receiving a shaft and on the other hand for the arrangement of the rotatable gear (4) is arranged thereon, for which the rotatable gear (4) has a to an axially extending central axis of the main gear (2) coaxial recess (17), and wherein the Main gear (2) with the rotatable gear (4) by means of a bayonet closure (14) is connected, characterized in that the bayonet closure (14) between the hub (5) and the rotatable gear (2) and / or between the hub (5 ) and one on the rotatable gear (4) adjacent the spring element (9) is formed.
    [2]
    2. gear arrangement (1) according to claim 1, characterized in that on the hub (5) radially outwardly projecting hub projections (15) are arranged.
    [3]
    3. gear arrangement (1) according to claim 2, characterized in that the hub projections (15) distributed symmetrically over the circumference of the hub (5) are arranged.
    [4]
    4. gear arrangement (1) according to one of claims 1 to 3, characterized in that in the axial direction between the hub projections (5) and the gear body (25) in the direction of the circumference of the hub (5) extending, undercut (23) is.
    [5]
    5. gear arrangement (1) according to claim 4, characterized in that the undercut (25) extends continuously over the circumference of the hub (5). N2010 / 22500
    [6]
    6. gear arrangement (1) according to one of claims 2 to 6, characterized in that the hub projections (15) in the circumferential direction (3) of the hub (5) have an overall length which is between 20% and 80% of the length of the circumference of the hub (5).
    [7]
    7. gear arrangement (1) according to one of claims 2 to 6, characterized in that the hub projections (15) viewed in the axial direction at least partially have a trapezoidal cross-section.
    [8]
    8. gear arrangement (1) according to one of claims 1 to 7, characterized in that in the recess (17) of the rotatable gear (4) and / or in a recess (50) of the spring element (9) radially inwardly projecting projections ( 16) are formed.
    [9]
    9. gear arrangement (1) according to one of claims 1 to 8, characterized in that the spring element (9) and / or the rotatable gear (4) has a rotation (54) / have.
    [10]
    10. gear arrangement (1) according to claim 9, characterized in that the rotation lock (54) is formed by at least one tab which engages in a recess (55) of the rotatable gear (4).
    [11]
    11. gear arrangement (1) according to claim 9, characterized in that the rotation lock (54) by at least one projection on the spring element (9) and / or on the rotatable gear (4) is formed.
    [12]
    12. gear arrangement (1) according to one of claims 2 to 11, characterized in that a transition between an end face of the hub (5) and the peripheral surface (38) in the region of the hub projections (15) is rounded or beveled.
    [13]
    13. A method for producing a bayonet closure (14) for a main gear (2) and a relative to this relative in the circumferential direction (3) rotatable N2010 / 22500 II -3- gear (4) having gear arrangement (1), wherein the main gear (2 ) has a gear body (25) on which in the axial direction above a hub (5) on the one hand for receiving a shaft and on the other hand for the arrangement of the rotatable gear (4) is arranged thereon, including the rotatable gear (4) one to an axially extending Central axis of the main gear (2) coaxial recess (17), characterized in that it comprises the steps: - sintered manufacturing a one-piece preform (39) for the main gear (2) from the gear body (25) and the hub (5) wherein on the circumference of the hub (5) starting from an end face of the hub (5), extending in the axial direction of the gear body (25) recesses (20) are formed, extending to one, the End face of the hub (5) extending in the axial direction opposite Ausnehmungsendwand (40), and each having two side walls (41,42) and a bottom surface (30), wherein at least one of the side walls (41,42) at an angle to the bottom surface (30 ) includes the recess (20) which is greater than 90 °; - Machining the hub (5) in the circumferential direction (3), whereby the Ausnehmungsendwände (40) are removed and partially undercuts (23) are formed, whereby hub projections (15) are formed, which form part of the bayonet closure (14).
    [14]
    14. The method according to claim 13, characterized in that the angle between the at least one side walls (41, 42) and the bottom surfaces (30) is selected from a range having a lower limit of 95 ° and an upper limit of 130 ° ,
    [15]
    15. The method according to claim 13 or 14, characterized in that at least individual edges, preferably all edges, the recesses (30) are rounded or beveled formed.
    [16]
    16. The method according to any one of claims 13 to 15, characterized in that the rotatable gear (4) is also made by sintering, wherein radially inwardly extending projections (16) in the recess (17) of the gear (2) are formed. N2010 / 22500 -4- ··· * * t * * * · Μ

    ♦ * * * * * * • * * I * * * * * * * ** #
    [17]
    17. The method according to claim 16, characterized in that on an in ra dialer direction extending end face (44) of the rotatable gear (2) an annular web (45) is formed. Miba Sinter Austria GmbH by lawyers

    Partner Attorney at Law N2010 / 22500
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE102005041357A1|2004-09-07|2006-04-06|Honda Motor Co., Ltd.|Shearing gear wheel for motor vehicle, has adjacent gear wheel with number of tooth whose tooth flank angle is coined to obtain laminar contact with each tooth of main gear wheel, and spring arranged between gear wheels|AT513613B1|2013-02-08|2014-06-15|Miba Sinter Austria Gmbh|gearing|
    AT518787B1|2016-07-18|2018-01-15|Miba Sinter Austria Gmbh|gearing|
    AT521375A4|2018-11-15|2020-01-15|Miba Sinter Austria Gmbh|gearing|US1554889A|1924-08-01|1925-09-22|William A Hutson|Antirattling gear|
    US4189951A|1978-06-27|1980-02-26|Bulova Watch Company, Inc.|Anti-backlash gear|
    US4273995A|1979-12-10|1981-06-16|Veeder Industries Inc.|Fuel pump counter transfer pinion|
    JPS611770U|1984-06-12|1986-01-08|
    JPH0141972Y2|1985-06-12|1989-12-11|
    US5113713A|1991-02-11|1992-05-19|United Technologies Corporation|Elastomeric load sharing device|
    DK0641621T3|1993-09-08|1998-05-25|Erowa Ag|Rotary drive device|
    DE9415460U1|1994-09-23|1995-07-20|Siemens Ag|Gear drive, in particular worm gear|
    JPH08159242A|1994-12-02|1996-06-21|Victor Co Of Japan Ltd|Backlashless gear structure|
    GB2305990B|1995-10-03|1999-05-26|Perkins Ltd|A method and a device for setting backlash between gears in a gear train|
    US5934144A|1996-06-10|1999-08-10|Active Automation, Inc.|Split gear assembly for use in a worm gear drive|
    US5813335A|1996-12-18|1998-09-29|Heidelberg Harris Inc.|Apparatus for preventing backlash between the meshing teeth of a first and a second gear in a printing unit of a lithographic rotary printing press|
    US5870928A|1997-05-08|1999-02-16|Cummins Engine Company, Inc.|Anti-lash gear with alignment device|
    US6148684A|1999-03-10|2000-11-21|Heidelberger Druckmaschinen Aktiengesellschaft|Anti-backlash gear|
    GB2360825B|2000-03-30|2004-11-17|Formflo Ltd|Gear wheels roll formed from powder metal blanks|
    IT250014Y1|2000-07-03|2003-07-07|Re M S R L|TOOTHED WHEEL STRUCTURE|
    JP3658369B2|2001-10-10|2005-06-08|キヤノン株式会社|Image forming apparatus|
    AT413748B|2004-03-22|2006-05-15|Miba Sinter Austria Gmbh|GEAR FOR A GAME-FREE HEAD WHEEL STAGE|
    JP4053528B2|2004-09-07|2008-02-27|本田技研工業株式会社|Scissor gear|
    WO2008142131A2|2007-05-21|2008-11-27|Vcst Industrial Products|Split gear for avoiding backlash when engaging a mating gear|
    CN101636601B|2008-03-28|2011-12-28|Nec显示器解决方案株式会社|Combination gear, lens adjusting mechanism and electronic equipment|
    AT506961B1|2008-09-09|2010-01-15|Miba Sinter Austria Gmbh|GEAR ARRANGEMENT|
    KR101047607B1|2008-12-05|2011-07-07|현대자동차주식회사|Caesars Gear|
    DE102009015953B4|2009-03-27|2012-09-20|Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Co. Kg|Rattle-free component pairing|
    AT510283B1|2010-09-29|2012-03-15|Miba Sinter Austria Gmbh|GEAR ARRANGEMENT|AT510283B1|2010-09-29|2012-03-15|Miba Sinter Austria Gmbh|GEAR ARRANGEMENT|
    DE102011122138A1|2011-12-22|2013-06-27|PMG Füssen GmbH|gearing|
    CN102829157A|2012-09-11|2012-12-19|力帆实业股份有限公司|Exhaust timing gear for engine|
    DE102012025210B4|2012-12-28|2014-08-14|Gkn Sinter Metals Holding Gmbh|Divided gear|
    DE102013009751A1|2013-06-11|2014-12-11|Daimler Ag|Spur gear for a valve train|
    AT514070B1|2013-06-11|2014-10-15|Miba Sinter Austria Gmbh|gearing|
    US9618108B2|2013-07-17|2017-04-11|Achates Power, Inc.|Gear noise reduction in opposed-piston engines|
    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|
    US10436303B2|2014-12-11|2019-10-08|Linamar Corporation|Scissor gear assembly with integral isolation mechanism|
    DE102015004454A1|2015-04-04|2016-10-06|Daimler Ag|Plate spring, in particular for a drive train of a motor vehicle, and drive train and method for mounting such a plate spring|
    NL2015189B1|2015-07-18|2017-02-07|Vcst Ind Products Bvba|Scissor gear assembly.|
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    CN201180044798.4A| CN103124867B|2010-09-29|2011-09-27|Geared system and for the manufacture of the method for bayonet type blocking mechanism|
    US13/823,898| US9297451B2|2010-09-29|2011-09-27|Toothed wheel arrangement and method for producing a bayonet fastening|
    EP11810994.1A| EP2622244B2|2010-09-29|2011-09-27|Gear wheel arrangement and method for producing a bayonet catch|
    PCT/AT2011/050014| WO2012040762A1|2010-09-29|2011-09-27|Toothed wheel arrangement and method for producing a bayonet fastening|
    BR112013007526A| BR112013007526A2|2010-09-29|2011-09-27|sprocket arrangement and process for making a bayonet closure|
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