• 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 friction gear for continuously variable speed control of the speed of an output shaft (9) which is driven by a driving input shaft (12), wherein between the input and output shaft (12, 9) a planetary gear or differential (1) is arranged, wherein a first component of the planetary or differential gear (1) with a first friction wheel (2) and the second component of the planetary or differential gear (1) with a first friction wheel (2) drehachsgleichen second friction wheel (3) is connected, wherein the second friction wheel (3) is drive-connected to the output shaft (9) and wherein the input shaft (12) is drivingly connected to a third component of the planetary or differential gear (1) with a friction disc (5) rotatable about a friction disc axis (5a), the friction disc axis (5a) normal to the axes of rotation (2a, 3a) of the friction wheels (2, 3) is arranged and the friction disc (5) parallel to the axis of rotation (2a, 3a) of the friction wheels (2, 3) versch is unbiebbar, and wherein the friction wheels (2, 3) can roll on the friction disc (5). In order to facilitate an interruption of the power flow to the output shaft in the simplest possible way, it is provided that the friction disc (5) in the region of the friction disc axis (5a) has a recess or depression (10) arranged concentrically with the friction disc axis (5a).
    公开号:AT510574A4
    申请号:T1072011
    申请日:2011-01-27
    公开日:2012-05-15
    发明作者:Johannes Dipl Ing Fh Rieger
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    • ···· · «· 4 · · - B-: 56136
    The invention relates to a friction gear for stepless Drehzahlregeiung the speed of a Ausgangswelie, which is driven by a driving input shaft, wherein between the input and output shaft, a planetary gear or differential gear is arranged, wherein a first component of the planetary or differential gear with a first friction wheel and the second component of the planetary or differential gear is connected to a second friction wheel drehachsgleichen to the first friction wheel, wherein the second friction gear is drivingly connected to the output shaft and wherein the input shaft is drivingly connected to a third component of the planetary or differential gear, with a friction disk to rotate a friction disk wherein the friction disc axis is arranged normal to the axes of rotation of the friction wheels and span with this a plane, wherein the friction disc is mounted parallel to the axis of rotation of the friction wheels in the plane, and wherein the friction wheels dense have a diameter and can abroil on the friction disc.
    From EP 9343 Al a friction gear with a counterbalance or planetary gear is known, which has two friction wheels with the same diameter, which abroil on a friction disc. The friction disk rotatable about a friction disk axis normal to the axis of rotation of the friction wheels is arranged to be longitudinally displaceable parallel to the axis of rotation of the friction wheels. By shifting the friction disc, the rolling radius of the friction wheels on the friction disc and thus the speed ratio between the first friction wheel and the second friction wheel changes. In this way, a continuous ratio between an input shaft and an output shaft can be realized. The friction discs each have an annular rolling surface for the friction wheels and are rotatably mounted about a non-rotatable shaft journal. The central region of the friction discs is thus not rotatable in each case. This causes the central friction wheel abruptly blocked as soon as this friction wheel - for example, when changing the direction of travel - comes into contact with the stationary shaft journal. Thus, at least when changing the direction of travel, an additional clutch for interrupting the power flow between the friction disc and the output shaft is required.
    The object of the invention is to avoid this disadvantage and to allow in a friction gear of the type mentioned in the simplest possible way a power flow interruption when changing the direction of rotation of the output shaft.
    According to the invention this is achieved in that the friction disc in the region of the friction disk axis aufwelst a concentric with the friction disk axis arranged recess or recess.
    Preferably, it is provided that the diameter of the circular recess or depression corresponds at least to the rolling width of at least one friction wheel, which is cut in at least one operating position of the friction gear of the friction disk axis.
    A possible low-wear change in the speed can be achieved if at least one friction wheel - viewed in a meridian section - has a curved convex Abrollbereich with a defined radius of curvature. For force flow interruption can be provided that the recess or recess has a curved concave surface, wherein preferably the radius of curvature of the surface substantially corresponds to the radius of curvature of the friction wheel.
    The diameter of the recess or depression is kept as small as possible in order to allow a bumpless start of the output shaft from the idle state. The radius in the region of the bottom of the recess or recess and in the region of the transition to the flat rolling surface of the friction disc allow a gentle acceleration from standstill.
    In order to enable a secure traction interruption, it is provided that the recess or depression has a defined maximum depth which corresponds at least to the indentation depth of the preferably elastically designed friction wheel.
    The rolling surface of the friction disc is designed to be substantially flat and closed, to allow a uniform change in the speed ratio between input and output times.
    Depending on the height of the maximum torque to be transmitted at least two, preferably at least three friction disks rotatable about a respective friction disk axis may be provided, whose friction disks arranged normal to the axis of rotation of the friction wheels have a common point of intersection on the axis of rotation of the friction wheels.
    A simple change in the speed ratio can be achieved if the friction disc is rotatably mounted on a parallel to the axis of rotation of the friction wheels slidably mounted disc carrier.
    The invention will be explained in more detail below with reference to FIGS.
    1 shows a friction gear according to the invention in a first operating position, FIG. 2 shows the friction gear in a second operating position, FIG. 3 shows the friction gear in a third operating position, FIG. 4 shows the friction gear in a fourth operating position, FIG fifth operating position and Fig. 6 shows an inventive friction gear in an end view in a variant.
    The mechanically infinitely variable friction gear mechanism shown in FIGS. 1 to 5 has a differential gear 1 and two friction wheels 2, 3, which are each connected to a friction wheel. The friction wheels 2, 3, the axes of rotation 2a, 3a are formed coaxially and have the same diameter D, are connected via the adjustable friction plate 5 by means of adhesion.
    The torque is introduced via the input shaft 12 on the ring gear 6 of the differential gear 1, which is connected to the differential housing 7, and is distributed over the Ausgteichsräder 8 on the wave wheels 4. The distribution of the torque on the wave wheels 4 is controlled by the position of the friction disc 5 and the resulting friction point radius r 2, r 3 of the friction wheels 2, 3 on the friction disc 5. Through a recess or depression 10 in the region of the friction disk axis 5a of the formed with a substantially flat rolling surface 5b friction disk 5, the adhesion for an idle position can be interrupted. The gear 11 is used to reverse the direction of rotation.
    In Fig. 1, the friction gear is shown in a first operating position, in which a translation is slow. The friction disc 5 is shifted so far to the left until the friction wheel 3 is outside the recess or recess 10 of the friction disc 5. This also leads to a frictional connection between the friction wheel 3 and the friction disk 5. The input speed of the ring gear 6 is distributed to the friction wheels 5 via the differential gear 1 to the friction wheels 2, 3 in the ratio of the current friction point radius rx to r2 on the shaft wheels 4. The friction wheel 3 and thus the output shaft 9 rotate slower than the input shaft 12th
    Fig. 2 shows a second operating position of the friction gear, in which the gear ratio between the rotational speed of the input shaft 12 to the rotational speed of the output shaft 9 corresponds to about 1: 1. The friction disc 5 is further shifted to the left until the friction point diameter r2, r3der the two friction wheels 2, 3 with the friction disc 5 have the same distance from the friction disc axis 5a. The input speed of the ring gear 6 is distributed over the differential gear 1 on the friction wheels 2, 3 in the ratio of the current friction point radii r2, r3 on the friction disc 5. The friction wheel 3 and thus the output shaft 9 rotate in a ratio of 1: 1 to the input speed of the ring gear 6. • · · · ··· »* ··« · · · · # «···· ···«
    Fig. 3 shows the friction gear in a third operating position in which a translation is done quickly. The friction disc 5 is moved even further to the left. The input speed of the ring gear 6 is distributed over the differential gear 1 on the friction wheels 2, 3 in the ratio of the current friction point radii r2, r3 on the friction disc 5. The friction wheel 3 and thus the output shaft 9 rotate faster than the rotational speed of the input shaft 12th
    4 shows the friction gear in a fourth operating position corresponding to the idling. At idle, the friction disc 5 is set so that the friction wheel 3 is cut from the friction disc axis 5a and through the recess or recess 10 in the Reibscheibenmitte no frictional connection with the friction disc 5 is. As a result, the entire input rotational speed of the ring gear 6 is guided in the friction wheel 2 and further on the friction disc 5. The friction wheel 3 and thus the output shaft 9 stand still.
    Fig. 5 shows the friction gear in a fifth operating position, which corresponds to the return gear. The friction disc 5 is shifted so far to the right until the friction wheel 3 is outside the recess or recess 10 of the friction disc 5. This also leads to a frictional connection between the friction wheel 3 and the friction disk 5. The input speed of the teler wheel 6 is distributed via the differential gear 1 to the friction wheels 2, 3 in proportion to the current friction point radii ri, r2 on the friction disk 5. The friction wheel 3 and thus the output shaft 9 rotate slowly and opposite to the input speed and input direction.
    The depth t of the depression 10 corresponds at least to the depth of impression of the friction wheels 2, 3 formed of elastic material. The width of the recess or depression 10 should correspond at least to the rolling width b of the friction wheels 2, 3. In order to achieve a punctiform contact surface with few friction losses between the friction wheels 2, 3 and the friction disc 5, each friction wheel 2, 3 in the rolling region 14 - viewed in a meridian section - executed concavely curved and has a defined radius of curvature r in Abrollbereich 14. In the exemplary embodiment, the surface of the recess or depression 10 is designed with a corresponding concave radius of curvature 3, which corresponds at least to the radius of curvature r of the friction wheels 2, 3 in the rolling region 14. As a result, on the one hand, a complete interruption of the power flow between the input shaft 12 and the output shaft 9 is achieved and, on the other hand, a smooth starting process is possible.
    In order to enable a bumpless and slow start-up of the output shaft 9 from the idle, the width B of the recess or recess 10 should be kept as small as possible.
    '-S:
    In order to transmit high torques between the input shaft 12 and the output shaft 9, a plurality of friction plates 10 may be provided. Fig. 6 shows a variant of a Reibradgetriebes with three friction plates 5, the Reibscheibenachsen 5a is arranged normal to the axes of rotation 2a, 3a of the friction wheels 2, 3, wherein the Reibscheibenachsen 5a with the axes of rotation 2a and 3a of the friction wheels 2, 3 each have a plane span ε. The friction disk axes 5a intersect in a common point S in the region of the axes of rotation 2a and 3a, respectively. All friction disks 5 are rotatably mounted in a common friction disk carrier 13 which is displaceable parallel to the axes of rotation 2a and 3a of the friction gear.
    The friction gear described allows a simple way a continuous speed adjustment, with high gear spreads can be realized. Through the recess or depression 10 in the region of the center of the friction disc, an idle position can be made possible, wherein a switchable during operation direction of rotation of the output shaft 9 and a decoupling of the output shaft of the friction disc 5 can be realized without the use of a separate clutch. For the change in the speed ratio between the input shaft 12 and output shaft 9, as well as the direction of rotation reversal only a single adjustment is required.
    权利要求:
    Claims (8)
    [1]
    1. Friction gear for continuously variable speed control of an output shaft (9) which is driven by a driving input shaft (12), wherein between the input and output shaft (12, 9) a planetary gear or differential (1) is arranged, wherein a first component of the planetary or differential gear (1) with a first friction wheel (2) and the second component of the planetary or differential gear (1) with a first friction wheel (2) drehachsgleichen second friction wheel (3) is connected, wherein the second friction wheel (3) is drive-connected to the output shaft (9) and wherein the input shaft (12) is drivingly connected to a third component of the planetary or differential gear (1) with a friction disc (5) rotatable about a friction disc axis (5a), the friction disc axis (5a) normal to the axes of rotation (2a, 3a) of the friction wheels (2, 3) is arranged and with this a plane (ε) span, wherein the friction disc (5) parallel to the rotation Axle (2a, 3a) of the friction wheels (2, 3) in the plane (ε) is displaceable, and wherein the friction wheels (2, 3) have the same diameter (D) and can roll on the friction disc (5), characterized the friction disk (5) has a recess or depression (10) arranged concentrically with the friction disk axis (5a) in the region of the friction disk axis (5a).
    [2]
    2. Friction gear according to claim 1, characterized in that the diameter (B) of the circular recess or recess (10) at least the Wälzbreite (b) at least one friction wheel (2, 3) corresponds, which in at least one operating position of the friction gear from the friction disk axis (5a) is cut.
    [3]
    3. Friction gear according to claim 1 or 2, characterized in that at least one friction wheel (2, 3) - viewed in a meridian section - a convexly curved Abrollbereich (14) having a defined radius of curvature (r).
    [4]
    4. Reibradgetriebe according to claim 3, characterized in that the recess or recess (10) has a curved concave surface, wherein preferably the radius of curvature (R) of the surface substantially the radius of curvature (r) of the friction wheel (2, 3) in Abrollbereich ( 14) corresponds.
    [5]
    5. Friction gear according to one of claims 1 to 4, characterized in that the recess or recess (10) has a defined maximum depth (t) which corresponds at least to the indentation depth of the friction wheel (2, 3).
    [6]
    6. Friction gear according to one of claims 1 to 5, characterized in that the friction disc (5) has a substantially flat, closed rolling surface (5b).
    [7]
    7. A friction gear according to one of claims 1 to 6, characterized in that the friction disc (5) on a parallel to the axis of rotation (2a, 3a) of the friction wheels (2, 3) slidably mounted disc carrier (13) is rotatably mounted.
    [8]
    8. A friction gear according to one of claims 1 to 7, characterized in that at least two, preferably at least three friction disks (5a) rotatable friction disks (5) are provided, whose normal to the axis of rotation (2a, 3a) of the friction wheels (2, 3) arranged Reibscheibenachsen (5a) have a common point of intersection (S) on the axis of rotation (2a, 3a) of the friction wheels (2, 3). 2011 01 27

    a-1150 Vienna, Marlehllfer Gürtel 39/17 Tel .: (t431) 13209 33 <0 füK (+43 1) 092 09 333 Fu / St
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    同族专利:
    公开号 | 公开日
    AT510574B1|2012-05-15|
    EP2481951A1|2012-08-01|
    US20120196717A1|2012-08-02|
    CN102619948A|2012-08-01|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US1402493A|1922-01-03|Variable-speed mechanism |
    US2936638A|1952-04-01|1960-05-17|Wassilieff Victor|Variable speed friction drive|
    DE1213190B|1962-11-08|1966-03-24|Grangier & Cie Ets|Friction gear change gear with several flat friction disks|
    FR2370200A1|1976-11-04|1978-06-02|Gkn Group Services Ltd|Steplessly adjustable drive unit - has disc faces pressed against peripheries of rollers on common axis|
    GB1600646A|1978-03-22|1981-10-21|Olesen H T|Power transmission having a continuously variable gear ratio|
    US4304154A|1978-09-05|1981-12-08|Gkn Group Services Limited|Variable ratio transmission mechanism|
    DE19643437C2|1996-10-22|1998-12-24|Volkswagen Ag|Infinitely adjustable gear|
    KR100469839B1|2002-07-16|2005-02-02|조광호|Nonstep variable speed device|
    EP1546580B1|2002-09-30|2013-07-17|Rohs, Ulrich, Dr.|Transmission|
    CN1752479A|2004-09-21|2006-03-29|王国斌|Slide palte deformed tooth stepless engagement adjustable gear|
    US7946944B2|2005-07-13|2011-05-24|Poongsung Construction Co., Ltd.|Electric continuously variable transmission and the driving method thereof|CN103791055B|2014-01-27|2016-01-20|沈阳建筑大学|A kind of automative stepless speed-variation device|
    CN105570420A|2014-11-03|2016-05-11|夏兴旺|Intersecting shaft type planet friction mechanical infinitely variable transmission and infinitely variable transmission method thereof|
    AT14788U1|2015-04-28|2016-06-15|Evloev Salman|Planet variator|
    CN111776637A|2020-07-06|2020-10-16|杨蕾|Intelligent feeder capable of stopping feeding and automatically dredging blockage based on gravity change|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    AT1072011A|AT510574B1|2011-01-27|2011-01-27|VARIATORS|AT1072011A| AT510574B1|2011-01-27|2011-01-27|VARIATORS|
    EP11195738A| EP2481951A1|2011-01-27|2011-12-27|Friction wheel transmission|
    US13/352,924| US20120196717A1|2011-01-27|2012-01-18|Friction gear|
    CN 201210025665| CN102619948A|2011-01-27|2012-01-29|Friction gear|
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