• 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:
    Stepless, positive gear with an input and an output, in which on a coupled to the drive, frusto-conical body (3), a portion of the circumference with a gear toothing (1) is provided, which serves for torque transmission. around the truncated cone (3) at least two counter-wheels (4) are arranged, which are displaceable parallel to the respective cone-generating end to change the transmission ratio along their shafts (5). The other portion (2) of the truncated cone (3) carries a special toothing, with the rotating truncated cone (3) for the establishment of the counter wheels (4) on the torque-transmitting toothing (1) is used. The mating wheels (4) have freewheels, and are, for example via other gears (6) on their support shafts (5) coupled to a gear (7) of the transmission output.
    公开号:AT513803A1
    申请号:T12262012
    申请日:2012-11-19
    公开日:2014-07-15
    发明作者:Thomas Dipl Ing Dr Sonnweber
    申请人:Thomas Dipl Ing Dr Sonnweber；
    IPC主号:
    专利说明:

    ♦ · · ···· • * ························································ · ♦ ··· ··· · ♦ ·· · ·
    DESCRIPTION
    Stepless, positive gear
    The invention relates to a continuously variable, positive gear with an input and an output.
    Stepless, positive gear in which on a truncated cone gear-toothing is attached, are known. For example, in DE20109297U1, a toothed rack is unwound helically over the conical surface. Here, however, on the one hand, the disadvantage that the teeth of the counter-wheels in driving truncated cone meet in an unregulated manner on the trailing teeth of the bolted teeth, because in the spaces between the teeth, the tooth pitch is not met, and on the other, that the teeth of the mating gears and the cone when moving the mating wheels parallel to the cone-generating (for changing the gear ratio) are laterally arbitrarily guided to each other, which in unfavorable case, a heavy use of the teeth during merging can cause.
    Explanation to the following text: The mantle of the truncated cone is divided in the circumferential direction into sections and along the height, starting from the head, into sections. 1 2/34 ··· · ··· · · · · · · · ······ ································································
    In the transmission according to the invention, a gear-like toothing 1 (for example an involute toothing) is mounted on the truncated cone 3 in a different way. It is seen in the circumferential direction, only a portion of the conical surface as a carrier of this torque-transmitting toothing 1 provided, the further area 2 of the conical surface is used to set up the counter wheels 4 on the rotation of the cone 3 again following torque-transmitting teeth 1 and does not serve the purpose to transmit a torque.
    At least two mating wheels 4 are installed around the cone, wherein a relative displacement of all mating wheels 4 is to take place together with respect to the truncated cone 3 along their respective conical generating ends to change the gear ratio. For this relative displacement of the counter wheels 4 and the cone 3, there are in principle different possibilities. The best solution appears to be that the mating wheels 4 are moved along their support shafts 5. It is also possible to provide each shaft 5 slidable in its axial direction and to move together with the respective mating gear 4. There are also solutions conceivable in which the transmission ratio is changed by moving the cone 3 in the axial direction and the shafts 5 are movable with the counter wheels 4 only in the radial direction or have universal joints in the upper area to be flexibly spreadable. 3/34 2
    The counter wheels 4 are coupled with the grating claw, which is made possible, for example, by a respective toothed wheel 6 seated on each of the shafts 5. These gears 6 then drive together a connected to the transmission output gear 7, which can be arranged above the head of the truncated cone 3. If a change of the gear wheels 4 is provided along its support shafts 5 to change the gear ratio, the shafts 5 and the truncated cone 3 are conveniently mounted rotatably in the stationary transmission housing.
    The counter-wheels 4 each have a freewheel which transmits the rotation transmitted by the cone 3 to the counter-wheel 4 in the direction of the transmission output.
    It would also be conceivable to provide the freewheels instead of on the counter-wheels 4, for example on the wheels 6 engaging in the wheel 7. This solution, however, appears to be less favorable.
    The teeth of the torque-transmitting toothing 1 tend to run in the direction of the cone-generating ends. Due to the retention of the tooth pitch with increasing cone circumference, depending on the specific position of a respective tooth, a deviation from this basic direction occurs. If a helical toothing is provided, the deviation additionally changes by its angle.
    The length of the teeth may extend over the entire conical surface, but in any case, it will be expedient to • ························································· • To be able to use at least one of the fleas of the conical mantle, at least one big egg.
    Instead of subdividing the cone circumference into only one torque-transmitting region 1 and one establishing region 2, it is also conceivable to provide these regions alternately over the circumference in each case several times. The advantage of several and thus narrower torque-transmitting regions 1 is that then turn out at their edges, the angle of the teeth in relation to the cone-generating smaller. However, it requires a vote with the number of mating wheels 4 and the width of the areas 1, so that at least one mating gear 4 is always in a torque-carrying area 1 in gear operation.
    In order that the area 2 of the circumference of the cone when the cone 3 rotates can periodically serve to join the torque-transmitting teeth 1 to the teeth of the counter-wheels 4, it is designed as follows:
    In a first section (as viewed from the conical head), the tooth spacing is expediently but not necessarily commensurate with the increasing circumference of the cone starting from a graduation which still corresponds to the normal division of region 1. The number of teeth thus remains constant and the teeth of the furnishing area 2 at the end simply reverts to the toothing of the torque-transmitting area 1. 5/34 4 ······································································· ··········· · · ·
    The mating wheels 4 rotate sicti * 'in this' section of the area 2 slower because of the larger tooth spacing and are therefore decoupled from the power flow by the corresponding provided freewheels. The resulting sliding relative movements between the teeth of the area 2 and the counter wheels 4, resulting from the larger pitch, burden the then largely force-free gears thus only insignificantly. Incidentally, with this solution, stepless, positive-locking transmissions can be designed for a smaller transmission range.
    The limit range of the possible spread of the pitch of the establishment area 2 is reached when there is a risk that in operation the tooth tips of the engaging teeth meet. This border area can be extended with the help of a special tooth form for the area 2 at least up to 1.4 times the normal tooth pitch.
    In order to enable a larger transmission range in the transmission according to the invention is now proposed to continue in a second portion of the area 2 only a portion of the teeth along the cone-generating, but leave another part to end. Specifically, for example, every second tooth can be continued. If this half of the teeth continues to run until it has reached a division of 1.5 times the normal division with a complete number of teeth at about the middle of section two (the previously stated limit of about 1.4 times 5 6 / 34 »· · · · · · · ··············································· · If not headings *, * only a part of the teeth are continued in this section), the continued teeth, after only every other tooth is present, have a spacing of three normal tooth pitches. However, this also corresponds to a gearing with normal division, in which only every third tooth is present (2 x 1.5 = 3). The mating wheels 4 can thus easily continue to rotate in this section of the region 2 with the speed transmitted from the torque-transmitting region 1, but only every third of their teeth engages in the remaining teeth.
    Furthermore, each of the continued teeth of section two may form each third tooth of a toothing, the number of teeth of which corresponds to the section two with complete number of teeth and normal pitch. This toothing has thus adapted its number of teeth the ever-increasing circumference of the cone by two new incipient teeth between the continued teeth again and marks the beginning of the third section of the area 2. Had the rest of the teeth of the area 2 less spread and maximized the factor For example, in section two instead of the above mentioned 1.5, for example, only set to 1.333, then only one third tooth would continue from section one of area 2, forming only every fourth tooth (3 x 1.333 = 4) of the gearing of section three. It would be in section two but again a gearing with normal pitch 7/34 6 •. However, only * ncTch * ^ e * # is the fourth tooth in this case would be present. The speed of the mating wheels 4 would thus not change in the transmission mode in this section again.
    In summary, section two serves the purpose of making section one end over before the tooth pitch becomes too large, and section three below it, with nearly normal tooth pitch (the pitch is actually slightly larger from section two) to start. Furthermore, the property that the distance of the remaining teeth in section two corresponds to an integer multiple of the normal distance, decisive for the fact that the mating wheels 4 can pass through this section in their transmission operation with their given from area 1 speed.
    Starting from the mentioned gearing at the beginning of the third section, the teeth of the area 2 are then in turn spread with increasing cone circumference. When the tooth distances in this section then approach a critical size again, a section four follows, into which, as in section two, again only a part of the teeth is continued.
    This repetitive procedure makes it possible to design a stepless, positive gear with any gear range. 8/34 7 · ♦ · ·
    On the other hand, the teeth of the torque transmission module 1 always have a normal pitch and are routed over the entire height of the cone. At the lateral edge to area 2 come with the increasing number of sections, the enlargement of the circumference of the cone accordingly, but gradually added new torque-transmitting teeth with normal pitch, making the area 1, while maintaining its pitch, over the entire cone height always almost the same Can cover the proportion of the cone circumference.
    On the truncated cone 3 shown in FIGS. 1 to 5 there is, for example, a torque-transmitting region 1 and a setting-up region 2, the region 2 having a total of three sections in which every second of the teeth ends at the top and between the continued teeth, start two teeth each time.
    Alternately with these sections, a total of four further sections can be seen, in which the teeth of the set-up teeth 2 spread with increasing cone circumference. It can also be seen the increase in the number of teeth of the torque-transmitting portion 1 with each new beginning of these four sections.
    The power flow of the transmission must run from the driven truncated cone 3 via the counter wheels 4 to the transmission output. A reverse flow of power from the counter wheels 4 on the cone 3 is not possible, because then the counter wheels in area 2 with increasing tooth spacing 9/34 8 · · · · # ·· would have to turn the cone faster * and 'som'it * the Free runs would not be relieving here, but in the area 1 with the normal toothing actually intended for torque transmission.
    Alternatively conceivable, however, would be to put by the drive the housing with the shafts 5 to a stationary cone 3 in rotation. It would then arise in conjunction with the gear 7 quasi a planetary gear, with the own rotational speed of the mating wheels 4 and thus the shafts 5 in turn could be regulated continuously.
    In the sections of the area 2, on whose upper or lower edge teeth run out or start again, it is recommended that, unlike in FIGS. 1 to 5 in simplified form, the ends of the departing or incipient teeth, as shown schematically in FIG shown to rejuvenate or round off. Characterized a sliding in of the teeth of the counter wheels 4 is facilitated in this section with a displacement of the counter wheels 4 to change the gear ratio of these teeth.
    The continuous teeth of the area 2 are shown in the illustrations 1 to 5 simplified with kinks in their course, but in fact these teeth should rather have a continuous curvature.
    FIG. 7 shows the interaction of the teeth of the counter wheels 4 and the teeth of the setting tooth 2 in two different positions. The toothing 2 of the 10/34 9 ··· ·· · · · · · · ······ · ························································································································································································ The distance of the teeth 2 is a value of about 1.4 times the normal pitch shown.
    It turns out that a special shaping is necessary for the teeth of the set-up toothing 2 (differently outlined in FIGS. 1 to 5) in order to be able to ensure a functioning intervention of the different toothings. To avoid collisions of the teeth in unwanted areas, it is recommended that the teeth of the set-up teeth 2 are lower than the teeth of the standard teeth 1. The purpose of a controlled continued sliding of the teeth 2 to cope with the increased tooth pitch serve a beveling of the teeth 2 in the rear region and a convex design of this back surface.
    Incidentally, FIG. 7 shows the two possible limit positions of the teeth 2, which have a certain play in relation to the toothing of the counter wheels 4. It can be seen for both positions that the interaction of the different gears for the purpose of setting up one another works (not for the purpose of torque transmission).
    FIG. 8 shows the interaction of the teeth of the counter wheels 4 with the transition region of the teeth of the setting tooth 2 and the torque transmitting tooth system 1 in two different positions. The driving cone with the teeth 1 and 2 rotates 11/34 ·· ·· · · · · • · · · * "·" ··· · • · ♦ · ····· * * m * '* l # ····· · · ι ····· * "here counterclockwise, therefore, again counterclockwise.
    It is shown at the distance of the teeth 2 again a value of about 1.4 times the normal pitch. It can be seen that the first tooth of the toothing 1, which has a normal pitch, should be shaped in a similar way to the teeth of the erecting toothing 2 in order to be able to ensure a smooth transition.
    FIG. 8 likewise shows the two possible limit positions of the teeth 1 and 2, which also have a certain clearance in relation to the toothing of the counter wheels 4. For both positions, it can be seen that the teeth 2 make it possible to set up the counter wheels 4 on the torque-transmitting toothing 1.
    Of practical use for the transmission operation, it could be the teeth of the establishing toothing 2 and also the first tooth of the torque-transmitting toothing 1 retractable and resilient, with the restoring suspension due to the existing centrifugal force effect may possibly be waived. The teeth of the set-up teeth 2 could then give in at a very unfavorable meeting with the teeth of the counter wheels 4.
    The body 3 is defined in protection claim 1 most commonly as a body tapering along its axis of rotation. For practical use, a rotationally symmetric ei , * KSgdlst * um, [ F as the most sensible solution, which is why in the protection claims and also in this description simplifies usually the term "truncated cone". or even easier "cone" used. This should not preclude the use of other bodies that taper along their axis of rotation for this purpose.
    By the way, the truncated cone 3 does not necessarily have to have straight generators. Curving inward or outward would change the characteristics of the transmission when changing the ratio. However, the production of the transmission would be more expensive and the mating wheels 4 with their shafts 5 would then have to be movable to change the transmission ratio in the radial direction.
    Alternatively, it would also be conceivable to attach the toothings of the regions 1 and 2 inside a hollow truncated cone. The mating wheels would then engage inside the truncated cone in the teeth. However, this solution appears to be considerably more complicated in terms of design.
    If the geometric and other parameters are fixed, the realization of a concrete transmission within the meaning of the invention certainly requires a certain amount of development work. Only then, for example, can the specifically optimal tooth shape of the establishing toothing of region 2 be designed. 13/3412 ···························································································.
    Basically, however, Bäsi'S * in * d * this letter proposed ideas should allow the construction of a perfectly functioning stepless, positive gearbox.
    Figures 1 to 4 show, each rotated by 90 ° clockwise, schematically in a view obliquely from above, a possible embodiment of the truncated cone 3 with the torque-transmitting toothing 1 (shown in darker) the setting toothing 2 (shown brighter).
    Figure 5 shows the main components of the transmission schematically in a general view from the front.
    FIG. 6 outlines a detail of the tooth shape of certain teeth of the furnishing area 2.
    FIG. 7 shows the interaction of the teeth of the setting toothing 2 and the counter wheels 4 in two different positions.
    Figure 8 illustrates the interaction of the transition region of the teeth of the establishing toothing 2 and the torque-transmitting toothing 1 with the teeth of the counter wheels 4 in two different positions. 14/3413
    权利要求:
    Claims (23)
    [1]
    ···· · «····· · · · · ············································································································································································································· Stepless, positive gear, characterized in that on the mantle of a rotatable, along its axis of rotation tapered body (3), such as a rotationally symmetrical truncated cone, one or more zahnradmäßige toothings (1) are provided, which serve to transmit torque in the circumferential direction, wherein the length of the teeth of these teeth (1) can correspond at least substantially to the length of the cone-generating, and that two or more gears are installed as counter-wheels (4) along the circumference of the truncated cone (3) to take over the rotational movement, wherein a change in the transmission ratio Displacement of the counter-wheels (4) and the truncated cone (3) is provided relative to each other, and that the torque-transmitting teeth (1) only one or more portions of the Kege Covering lumfangs, while one or more further portions (2) of the conical periphery have a special toothing, which serves to set up the counter wheels (4) on the teeth of the periodically following in transmission operation torque transmitting portions (1).
    [2]
    2. Transmission according to claim 1, characterized in that the torque-transmitting areas (1) and the establishing areas (2) are arranged alternately around the circumference of the truncated cone (3). 15/3414 · · · ···· • ··· · · · · · ······
    [3]
    3. Transmission according to one or more cfer 'previous protection claims, characterized in that the counter wheels (4) each have a freewheel.
    [4]
    4. Transmission according to one or more of the preceding claims, characterized in that each mating gear (4) in each case via its freewheel and its carrier shaft (5) is coupled to the transmission output.
    [5]
    5. Transmission according to one or more of the preceding claims, characterized in that the counter wheels (4) are evenly distributed around the circumference of the conical stump (3).
    [6]
    6. Transmission according to one or more of the preceding claims, characterized in that each axis of rotation of a counter-wheel (4) runs parallel to the cone-generating, against which the counter-wheel (4).
    [7]
    7. A transmission according to one or more of the preceding claims, characterized in that the relative displaceability of the counter-wheels (4) and the truncated cone (3) is arranged to change the gear ratio so that each mating gear with respect to the truncated cone (3) always in the same height as the other mating wheels.
    [8]
    8. Transmission according to one or more of the preceding claims, characterized in that the counter wheels (4) for changing the gear ratio- 16 / 34-5 «· ♦ ·· · · · ···· ······· · ···················································································································································································································································· ,
    [9]
    9. Transmission according to one or more of the preceding claims, characterized in that the toothing of the setting-up area (2) has one or more sections along the cone height, in which increase the tooth spacing of the toothing with increasing circumference of the cone (3).
    [10]
    10. A transmission according to one or more of the preceding claims, characterized in that the toothing of the furnishing area (2) has one or more sections along the height of the cone through which only a part of the teeth is continued, while the other part of the teeth on upper or lower edge of these sections ends or begins.
    [11]
    11. A transmission according to claim 10, characterized in that the width of these sections corresponds at least to the width of the toothing of the counter wheels (4).
    [12]
    12. A transmission according to one or more of claims 10 and 11, characterized in that the teeth of the establishing toothing (2), which ends in these sections or begin to taper at the ends or are rounded.
    [13]
    13. Transmission according to one or more of claims 10 to 12, characterized in that the distance of the 17/3416 • ···················································· ···· ································································································································································································································································ Gearing of the torque-transmitting area (1) corresponds.
    [14]
    14. A transmission according to one or more of claims 10 to 12, characterized in that the distance of the teeth continued through these sections, in the respective section, as exactly as three times the pitch of the toothing of the torque transmitting area (1) corresponds, and that of the Teeth about every second ends and start at the teeth underneath between the continued teeth in each case two new.
    [15]
    15. A transmission according to one or more of claims 10 to 12, characterized in that the distance of the teeth continued through these sections, in the respective section, as exactly as four times the pitch of the toothing of the torque transmitting area (1) corresponds and that of the teeth on each of two of three ends and in the teeth underneath between the continued teeth each start three new.
    [16]
    16. Transmission according to one or more of the preceding claims, characterized in that the teeth of the establishing toothing (2) have a lower height than the teeth of the normal toothing of the region (1). 18/3417 · · · · · · «····· · · · · ······················································································
    [17]
    17. Transmission according to one or more cter * preceding claims protection, characterized in that the teeth of the establishing toothing (2) seen at its, seen from the direction of rotation, bevelled and / or ver extended and convex in comparison with the tooth shape of the standard toothing can.
    [18]
    18. A transmission according to one or more of the preceding claims, characterized in that the one or more, seen from the direction of rotation, the first teeth of the teeth having a normal pitch (1) have a lower height than the teeth of the normal toothing.
    [19]
    19. A transmission according to one or more of the preceding claims, characterized in that the one or more, seen from the direction of rotation, the first teeth of the normal pitch having a toothing (1) on its, seen from the direction of rotation, back in comparison to the tooth shape of Standard teeth are chamfered and / or elongated and may be convex.
    [20]
    20. Transmission according to one or more of the preceding claims, characterized in that the teeth of the establishing toothing (2) are at least partially retractable movable and possibly also spring-mounted. 1 Q 19 / 34'e • ····· »····· ♦ · · · · · · · · · · · · · · · · · · ··········································· ·· ♦ ·
    [21]
    21. Transmission according to one or more Her * previous claims protection, characterized in that the one or more, seen from the direction of rotation, the first teeth of the normal pitch having a toothing (1) are at least partially retractable movable and possibly also resiliently mounted.
    [22]
    22. Transmission according to one or more of the preceding claims, characterized in that in the transmission mode alternatively not the cone (3) is driven and thus set in rotation, but that the shafts (5) bearing housing by the drive in rotation to the stationary Cone (3) is offset and the rotation is then passed through the driven counter gear wheels (4) to the transmission output.
    [23]
    23. A transmission according to one or more of the preceding SchutzanSprüche, characterized in that the described areas 1 with the torque-transmitting teeth and serving to set up the counter-wheels areas 2 are alternatively not on the outside of the jacket of a truncated cone, but on the inner shell of a along its Rotary axis tapered hollow body, such as a hollow cone stump, are mounted, and that the counter-wheels engage in this case in the interior of the hollow body in the teeth. 20 / 34-9
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    同族专利:
    公开号 | 公开日
    DE102013019123A1|2014-05-22|
    AT513803B1|2016-09-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    GB191007989A|1910-04-02|1911-01-19|Waclaw Czerniewski|Improvements in or relating to Variable Speed Gears.|
    WO1989009895A1|1988-04-12|1989-10-19|Juan Lloveras|Gear apparatus|
    WO2004059190A1|2002-12-31|2004-07-15|Seok-Bong Nam|Machinetype transmission for a car|
    CN104595430A|2015-02-03|2015-05-06|任孝忠|Stepless speed change device of staggered speed change rack|
    CN104864043B|2015-06-08|2018-01-05|任孝忠|Double ratchet-gear wheel stepless speed change devices|
    法律状态:
    2018-07-15| MM01| Lapse because of not paying annual fees|Effective date: 20171119 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA1226/2012A|AT513803B1|2012-11-19|2012-11-19|Stepless, positive gear|ATA1226/2012A| AT513803B1|2012-11-19|2012-11-19|Stepless, positive gear|
    DE201310019123| DE102013019123A1|2012-11-19|2013-11-15|Stepless, positive gearbox, has truncated cone whose set of circumference portions comprises gearing that is arranged along height of cone in portions, where spacing of gearing is larger in portions with increasing circumference of cone|
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