• 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:AT510281A4
    申请号:T17852010
    申请日:2010-10-28
    公开日:2012-03-15
    发明作者:
    申请人:Puchhammer Gregor Dr；
    IPC主号:
    专利说明:

    2
    The invention relates to a wobble gear, which is arranged on a drive shaft wobble body with at least one row of power transmission elements, in particular sprockets, with the input side and output side arranged secondary power transmission elements, in particular sprockets interaction.
    Such known transmissions for high reduction ratios are based on the idea of a differential gear in which two sprockets with a few teeth difference are shifted from each other. The first sprocket is usually rigidly connected to the housing, whereas the second sprocket is connected to the drive shaft.
    The aim of the invention is in particular to obtain a backlash-free or almost backlash-free transmission. 15
    This is achieved primarily by the fact that the drive shaft is divided, wherein the first part of the drive shaft is mounted axially fixed in the housing via a bearing and the second part of the drive shaft is axially slidably connected to the first part so that torques are transferable, further the wobble body is disposed on the axially displaceable part of the drive shaft 20 and the angle between the wobble body and the drive shaft axis is variable.
    By pivoting the wobble body, the sprockets of the wobble body are pressed on both sides in the corresponding teeth. 25 The respectively engaged tooth flanks of the corresponding gears therefore contact on both sides of a tooth, whereby the backlash between the tooth flanks of both wheels goes to zero
    The pivoting of the wobble body can be used as a compensation for occurring manufacturing tolerances 30 to minimize the backlash at the points of engagement of the gears in the transmission or to stop altogether. If the tumbling body is moved in the other direction of swiveling, and thereby the tumbling angle is reached, the tumbling angle 3 3.... I ·· t ················································································································································ This causes a disengagement of the wobble body and thus disengaging the output shaft.
    Furthermore, by measuring the wobble angle or measuring the change in the wobble angle, a measured value can be determined which can be used as a measure of the torque transmitted in the transmission. Such a measurement can also be used for other tasks, such. As regulation and control can be used.
    Further features of the invention are highlighted in the following description of embodiments, to which the invention is by no means limited.
    FIGS. 1 to 5 show longitudinal sections of wobble gears according to the invention, and FIGS. 6 and 7 show spring characteristics. FIGS. 8 to 11 show two embodiments of a jointless arrangement.
    According to FIG. 1, a two-part drive shaft 1, 2 is arranged in a wobble gear, wherein the first part 1 of the drive shaft is axially fixed in the housing 10 via a bearing 3 and the second part 2 of the drive shaft is connected to the first part 1 in an axially displaceable manner is that torques are transferable. The connection between the two parts 1 and 2 takes place in the drawn Ansführungsbeispiel by a bolt 4 which is axially displaceable in a groove 5 of the part 2.
    On the axially displaceable part 2 of the drive shaft, there is a pin 6 which rotates cyclically with the drive shaft 1,2. A wobble body 7 is mounted on this pin 6 and forms with the axis of the drive shaft 1.2 an angle, the wobble angle φ. The wobble body 7 is located in the middle between a fixed bevel gear 8 and acting as an output shaft bevel gear 9. The fixed bevel gear 8 is torsionally rigidly connected to the housing 10, in the case shown via a positive connection. 4
    The wobble body 7 is provided on both sides with a sprocket 11 and 12, which sprockets 11 and 12 with the bevel gears 8 and 9 Collaborate.
    According to the invention, the angle between the wobble body 7 and the drive shaft 1,2 should be actively or passively changed. As a result, a backlash-free transmission is to be obtained.
    By pivoting the wobble body 7, the sprockets 11 and 12 of the wobble body 7 are pressed on both sides in the corresponding teeth of the bevel gears 8 and 9. The respectively engaged tooth flanks of the corresponding gears therefore contact on both sides of a tooth, whereby the backlash between the tooth flanks of the pair of wheels approaches zero. This pivoting of the wobble body 7 can (and should, of course) as compensation for the general occurring in a production
    Manufacturing tolerances are used to minimize the backlash at the points of engagement of the teeth of the gears 8,9 and 11,12 in the transmission or to stop completely. If the wobble body 7 is rotated in the other pivoting direction (reduction of the wobble angle < p), the tooth flanks come out of contact. This causes a disengagement of the wobble body 7 and thus a disengagement of the output shaft (bevel gear 9), resulting in a coupling mechanism as an additional effect. This just mentioned pivoting of the wobble body 7 in the opposite direction can be done both by targeted use of the passive tooth forces, as well as by active influence by means of a mechanism. The purpose of this additional function is disengaging without load or under load. This function can also be used as overload protection under load. In addition, the change in the swivel angle φ or the swivel angle itself can be considered as a measure of the internally occurring tooth forces, which work against an elastic element 13 (or the inherent elasticity of the entire assembly). By measuring this swivel angle φ or the measurement of the change in the swivel angle φ, there is a measured value which can be used as a measure of the torque transmitted in the transmission. The measurement can be used for other tasks (control, control, ...). 5 «* *» · · · »# * * • · · · · · · · ·« · · · · · · ···
    In the exemplary embodiments according to FIGS. 1 and 2, the wobble body 7 is pressed into the desired position by an Allen screw 14 or by the elastic element 13 (FIG. 1). The end position may be obstructed by a stop to set a desired tooth air, e.g. to achieve a desired smooth running of the transmission or a desired play in the output. This stop is formed by an Allen screw 15 (Figures 1 and 2).
    According to FIG. 1, a segment 16 lying in a groove can also be provided, which obstructs the tilting movement after a smaller tilting angle. As a result, tilting out of the wobble body 7 is prevented under moment load.
    In Fig. 3, an embodiment for the active control of the angle φ of the wobble body 7 is shown. By means of a pulling member 17, a bearing 18 is axially displaced, the inner ring is connected to the pivotable wobble body 7. By axial displacement of the linkage 17 of the wobble angle φ can be controlled directly.
    According to Figure 4, the change of the swash angle φ can also be done by a hydraulic or pneumatic actuator. In this arrangement, a piston 19, which is guided in a cylindrical bore, presses on the wobble body 7 and this tilts into the counter-toothing. The application of the piston 19 takes place via the part 2 of the drive shaft.
    In the embodiment according to FIG. 5, the wobble body 7 is articulated on an elastic element 20. This could simultaneously combine the angular mobility around the wobble axis and the spring action. Stop elements 21 can be installed in addition to increase the contact pressure or to define end stops for both tilting directions. These can be incorporated as separate elements in the transmission. 6 • »« «· · · ·« • * «· > * • ί · · t · · t • • • • • • • • • • • • • • •
    If the elastic element 20 is formed, for example, by an elastomer, this results in additional possibilities of movement of the wobble body 7 in the radial and axial direction. These movement options can be used to change the efficiency and thus to allow self-locking of the transmission.
    To the wobble body 7 act on both sides (diagonally opposite) tooth forces that are proportional to the applied output torque. These tooth forces cause the elastic element 20 a displacement of the wobble body 7 in the radial or axial direction. By this shift also changes the (exact) Abrollkinematik the wobble mechanism, the wobble center of the wobble body 7 is no longer the imaginary apex of the bevel gears 8.9, but an undefined Taumelzentrum. This results in additional parasitic tooth forces between the contacting tooth flanks, which are not involved in the torque transmission. It can lead to jamming of the tooth flanks and thereby to a significant reduction in the overall gear efficiency, so that self-locking can occur.
    In FIGS. 6 and 7, the characteristics of possible elastic elements 13, 20, 22, 23 are shown, namely the course of the moment acting on the wobble body is plotted as a function of the wobble angle φ.
    Curve a: The wobble body 7 is pressed in the maximum possible end position (wobble angle φ max) with a bias in the toothing. As a result, freedom of play is guaranteed even with no load of the transmission. With increasing moment M (reduction of the wobble angle φ), the spring force increases.
    Curve b: The increase in the spring force is degressive in this case. When a maximum load is exceeded, the wobble body 7 completely tilts out of engagement and disengages the toothing. This can be used as a safety function. An advantage here is that the coupling process happens very suddenly and the gearing is spared. 7 «· 4 · * ·« «4 4 4 4 4 4» «« ·· 4 4 4 4 · * 4 «ι« 4 4 4 * * it · 4 * · 4 · 4 4 · «· · · 44 444 44 · 4 44 «4
    Curve c: The wobble body 7 has a neutral position, which does not correspond to the maximum tilt position. By changing the angle at which the moment zero crossing occurs, the backlash can be influenced and adjusted.
    Curve d: The torque characteristic consists of composite characteristics. This is the general case. As a result, the behavior of the transmission can be specifically influenced. The characteristic segment dl shows a hard mechanical stop in the gearbox, which can be used to set a minimum of tooth air. The characteristic curve d3 shows a compared to dl softer stop in the transmission, which hinders, for example, a complete disengagement of the teeth even under heavy load.
    Curve e: It shows the general case of an exponential moment curve. Here, a moderate transition can be created between the play-free ease of transmission without load and the ability to transfer even large forces in the transmission can. The efficiency can be increased at low loads.
    Curve f: As with curve e, a continuous but degressive characteristic can be used. Possible advantages: The transmission has a play-free, stiff transmission behavior even at low loads, but the maximum possible torque is limited.
    Curve g: It is also possible to incorporate a hysteresis in the characteristic curve. This can be done, for example, with elastomers or frictional elements. An advantage of this configuration is that the engagement (after a previous disengagement) is very gentle. This serves to protect the teeth.
    8 and 9 show an arrangement of the drive shaft 2 and the wobble body 7 with a further resilient mounting. All other transmission elements are not shown.
    δ
    A cross-shaped leaf spring 22 is fixedly connected both to the drive shaft 2 and to the wobble body 7. The connection between the drive shaft 2 and the leaf spring 22, and between the leaf spring 22 and the wobble body 7 is non-positively or positively executable. It can consist of one or more parts 5. This shape of a cross-type leaf spring 22 can produce the required torsion spring forces. An installation of the wobble body 7 under bias of the leaf spring 22 is possible.
    At the same time, this arrangement is stiff against axial or other displacements. 10 This makes it easy to replicate a swivel joint. The required rotary softness is given.
    Figs. 10 and 11 show a similar arrangement. Here are achieved by two spring wires 23, the suspension properties. Again, a rotation of the tumbling body 7 is possible, a shift in any direction is hardly possible.
    It is essential that the backlash can also be achieved by hingeless arrangements, which allow tilting of the wobble body 7 on the input shaft. In addition, this can be done in combination with a force generated by this arrangement 20, acting on the wobble body 7 spring force.
    Numerous modifications are possible within the scope of the invention. Thus, the connection of parts 1 and 2 could be e.g. done by a bellows.
    权利要求:
    Claims (10)
    [1]
    9 • ** «« ♦♦ * · · • · «« 4 «• · > 1. wobble gear whose arranged on a drive shaft (1, 2) wobble body (7) with at least one row of power transmission elements, in particular sprockets (11, 12) is provided with the input side and output side arranged secondary power transmission elements, in particular sprockets (8,9) interaction, characterized in that the drive shaft (1,2) is divided, wherein the first part (1) of the drive shaft (1,2) via a bearing (3) fixed axially in the Housing (10) is mounted and the second part (2) of the drive shaft (1, 2) axially slidably connected to the first part (1) is connected so that torques are transferable, further, the wobble body (7) on the axially displaceable part ( 2) of the drive shaft (1,2) and the angle (q>) between the wobble body (7) and the drive shaft axis is changeable.
    [2]
    2. wobble mechanism according to claim 1, characterized in that the wobble body (7) on a drive shaft (1,2) transversely passing, as a bolt (6) formed joint axis is mounted.
    [3]
    3. wobble mechanism according to claim 1, characterized in that the wobble body (7) via an elastic element (20) on the drive shaft (1,2) is mounted.
    [4]
    4. wobble mechanism according to one of claims 1 to 3, characterized in that in the sense of a pivoting of the wobble body (7) acting pivot member (14, 15, 13) is arranged.
    [5]
    5. wobble mechanism according to claim 4, characterized in that the pivoting member is a screw (14, 15).
    [6]
    6. wobble mechanism according to claim 4, characterized in that the pivoting member a stop element (16), e.g. is a lying in a groove segment (16). V

    10
    [7]
    7. wobble mechanism according to claim 4, characterized in that the pivot member is an approximately parallel to the drive shaft axis acting tension member (17) which acts on the wobble body (7). 5
    [8]
    8. wobble mechanism according to claim 4, characterized in that the pivot member is a hydraulically or pneumatically actuated element or a piston (19) which engages the wobble body (7).
    [9]
    9. wobble mechanism according to one of claims 3 to 8, characterized in that the elastic element is a cross-like leaf spring (22).
    [10]
    10. wobble mechanism according to one of claims 3 to 8, characterized in that the elastic element consists of wire springs (23). 15 Vienna, October 25, 2010 Gregor Puchhammer



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    同族专利:
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    引用文献:
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    法律状态:
    2017-06-15| MM01| Lapse because of not paying annual fees|Effective date: 20161028 |
    优先权:
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