• 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:
    A transmission arrangement with two identical epicyclic gearboxes (1, 2), each having three shafts (3, 4, 5), between a transmission input (6) and a transmission output (7) is described, one of the three pairs of corresponding shafts (3, 4, 5) of the two planet gears (1, 2) a pair of shafts (3) the Getriebeein- and output (6, 7) is assigned, while the shafts (4, 5) of the other two shaft pairs together in a rigid, opposite gear ratio are drive connected. In order to ensure an extensive free translation, it is proposed that the two shaft pairs of rigidly drive-connected shafts (4, 5) have an opposite, but equal transmission ratio and that at least one of the shaft pairs of rigidly drive-connected shafts (4, 5) to a device (1 0) is connected to the torque application.
    公开号:AT517618A4
    申请号:T50780/2015
    申请日:2015-09-10
    公开日:2017-03-15
    发明作者:
    申请人:Johann Kropfreiter；
    IPC主号:
    专利说明:

    The invention relates to a transmission arrangement with two equal, three shafts having epicyclic gearboxes between a transmission input and a transmission output, wherein of the three pairs of corresponding shafts of the two epicyclic gear a pair of waves is assigned to the Getriebeein- and output, while the waves of the two remaining shaft pairs are drivingly connected together in a rigid, opposing gear ratio.
    In order to obtain infinitely variable in their speed, mechanical transmission arrangements, it is known to provide two differently coupled to each other epicyclic between a Getriebeein- and output and to control, for example by applying individual gear members with a braking torque so that the output side, a desired speed established. However, the possibilities of influence on the gear ratios remain limited.
    In a transmission assembly used as a torque converter with two equal, three shafts having epicyclic between the Getriebeein- and output, it is also known (DE 26 35 946 A1), not the Getriebeein- and output associated, corresponding to each other waves of the epicyclic gears to couple with each other via a rigid drive connection, wherein the rigid drive connections between the two corresponding pairs of shafts have an opposing translation with a product of the two ratios Φ 1, so that due to the prescribed between the two planetary gear ratios at constant drive conditions, an independent adjustment of the speed and Torque takes place on the transmission output side to the loads occurring there. Due to the unequal product of the predetermined translation of
    Zungsverhältnisse the two rigid drive connections between the two epicyclic gearboxes is determined by the speed of the transmission output shaft, the movement of the two planetary gear unique, which precludes a further influence on the output speed.
    The invention is therefore an object of the invention to provide a gear assembly that allows a substantial influence on the respective overall translation and thus an adjustment to different transmission requirements.
    Starting from a gear arrangement of the type described above, the invention solves the problem set by the fact that the two shaft pairs of rigidly drive-connected shafts have an opposite but the same gear ratio and that at least one of the shaft pairs of rigidly drive-connected shafts is connected to a device for Drehmomentbeaufschlagung ,
    According to the same, but opposing gear ratios of the two rigid drive connections between the two planetary gears, which is expressed in a product of the two ratios equal to 1, the speed of the output shaft can be chosen regardless of the speed of the drive shaft, because required by the two in the required Way with each other drive-connected epicyclic gearbox always a balance between the speeds of the input and output shafts of the gear assembly due to the circumstance is possible that adjusts a gear ratio corresponding to the speed ratio of the input and output shafts in the region of the two epicyclic gear. However, this also means that desired rotational speeds can be ensured on the output side of the transmission arrangement by a corresponding influence on the two drive-connected epicyclic gearboxes despite predetermined drive conditions on the input side. Such influencing is possible by a device for applying torque to at least one of the shaft pairs of the drive-connected shafts rigidly connected to each other, wherein, depending on the requirements, an application with a preferably controllable braking or acceleration torque may be required. In the case of application of an acceleration torque, advantageous design conditions result if the acceleration torque is derived from the shaft of the transmission output or of the transmission input so as not to have to provide a separate drive.
    Because of the same but opposite translation ratios in the range of the two pairs of waves of rigidly connected drive shafts a short and over the other pair of waves is given a long translation on the one pair of waves. Accordingly, if the shaft pair is stopped with the short ratio, the result is a high speed corresponding to the long transmission of the other shaft pair for the output shaft of the transmission arrangement. By stopping the shaft pair with the long gear ratio, the short gear ratio becomes effective. With a connected to the shaft pair with the short translation means for applying torque thus the ratio of the gear assembly can be increased over that of the long translation. This means with a corresponding derivation of an acceleration torque from the output shaft, that the output shaft is accelerated to the highest speed.
    If, in contrast, the shaft pair with the long gear ratio is connected to a device for applying torque with a braking torque, the rotational speed of the output shaft is reduced as a function of the braking torque, which is important when using such a gear arrangement in a vehicle, for example for downhill driving. The rotational speed of the output shaft thus depends on the magnitude of the acceleration torque acting on the shaft pair with the short ratio on the one hand and the braking torque acting on the shaft pair with the long ratio on the other hand for a given load torque.
    Thus, the braking torque can be set sensitively to the shaft pair with the long translation, the device for torque application of the rigidly drive-connected shafts with the long translation an additional rigid drive connection of these two waves with an approximately same, but different gear ratio include, one of the two Shafts between the two drive connections comprises means for transmitting a limited torque. Due to the different transmission ratios of the two drive connections, the shaft pair is held rotationally fixed by the two drive connections, as long as the means for transmitting a limited torque does not allow relative rotation of the two interconnected by the device shaft parts. When the limit torque is exceeded, a rotation of the shaft pair is permitted, wherein the difference in the gear ratios of the two drive connections between the shafts of this shaft pair determines the sensitivity of the Bremsmomentbeaufschlagung.
    As already stated, because of the special coupling of the two epicyclic gearbox, a rotation independent of the rotation of the input shaft rotation of the output shaft of the gear assembly is possible, so also reversing the direction of rotation when the two Umlaufrädergetriebe are controlled accordingly via the means for applying torque, but with a corresponding Construction effort is connected. Simpler design conditions arise when the transmission output associated shaft is drivingly connected to a shaft of a three-shaft epicyclic gear, of the two other waves of Umlaufrädergetriebes a shaft forms an output shaft and the other shaft is acted upon by a torque, so that this additional epicyclic gear Forming gear, with the help of the shaft of the gear output, a rotational movement is superimposed, which determines the speed and direction of rotation of the output shaft.
    In the drawing, the subject invention is shown, for example. Show it
    1 shows a gear arrangement according to the invention in a schematic block diagram,
    FIG. 2 is a representation corresponding to FIG. 1 of an embodiment variant of a gear arrangement according to the invention, FIG.
    Fig. 3 shows a further embodiment of a transmission arrangement according to the invention and
    Fig. 4 shows a transmission arrangement according to the invention with an additional summing gear.
    The gear arrangement according to FIG. 1 comprises two epicyclic gearboxes 1,2 each having three shafts 3,4 and 5, wherein the shaft 3 of the epicyclic gearbox 1 is associated with the gearbox input 6 and the shaft 3 of the epicyclic gearbox 2 with the gearbox output 7. The shafts 4 of the one and the shafts 5 of the other shaft pair are connected to each other via rigid drive connection 8, 9, which have opposing, but equal translations, so that the product of the two ratios is equal to 1. Due to these opposing gear ratios results from the rigid drive connection 8 a short and by the drive connection 9 a long translation between the two planetary gears 1,2, with the result that at a non-rotatable holding the drive connection 8, the planetary gear 2 via the long translation of the drive connection and when stopping this drive connection 9, the planetary gear 2 is driven via the short ratio of the drive connection 8.
    By a device 10 for applying torque, for example, the shaft pair 4 can thus be influenced on the gear ratio of the gear assembly. If no torque is exerted on the drive connection 6 via the device 10, the shafts 4 can thus be moved independently of the device 10, then the output-side shaft 3 of the epicyclic gearbox 2 can be independent of the input-side shaft 3 of the epicyclic gearbox 1 with respect to the rotational speed and the direction of rotation be moved because automatically sets a gear ratio corresponding to the speed ratio of the two shafts 3 within the two epicyclic gearbox 1.2 due to the existing degrees of freedom. However, this means at the same time that can be adjusted by a means 10 for the corresponding torque application of at least one of the shaft pairs 4 and 5, any gear ratio of the gear assembly.
    In the illustrated embodiments, the epicyclic 1.2 are shown as a planetary gear, which is not mandatory, as it is not necessary to use the web 11 of the planetary gear bearing waves 3 as input and output side waves, because this is the other two Waves 4.5 of the planetary gear 1,2 are suitable. 1, the web 11 of the planetary gear 1 is driven by a drive shaft 12 via a gear 13. Of the usually distributed over the circumference of the sun gear 14 arranged planetary gears 15 of the epicyclic gearbox 1.2 is indicated for clarity, only one. The sun gear 14 supporting shafts 4 and the shafts 5 for the ring gear 16 are rigidly connected to each other via the drive connections 8, 9, wherein each of these used gear pair 17,18 can be replaced by another type of drive connection with a suitable translation, z , B. by a chain or belt drive. The output-side shaft 3 of the planetary gear 2 is connected symmetrically to the transmission input 6 via a gear 19 with an output shaft 20 according to the embodiment. At a predetermined speed of the drive shaft 12 thus the speed of the output shaft depends on the setting of the device 10, which acts according to the Fig. 1, the sun gear 14 of the planetary gear 2 with a corresponding braking torque. Since it only depends on the action of the waves 4 with a braking torque, the device 10 can be structurally different and z. As a brake, a slip clutch or a torque converter, preferably with a continuous adjustment include.
    The embodiment of FIG. 2 differs from the transmission arrangement according to FIG. 1 essentially only in that the means 10 for applying torque to the shafts 4 of the epicyclic gearboxes 1,2 with a
    Applied acceleration torque, which is derived from the output shaft 20. For this purpose, the device 10 is connected via a meshing with the gear 19 gear 21 to the output shaft 20 and connected via a drive connection 22 with the shaft 4 of the planetary gear 1. As long as the full torque is transmitted to the drive connection 22 via the device 10, the drive connection 8 is accelerated with the effect that the speed of the output shaft 20 increases. Only when the transmittable by the device 10 torque is exceeded, the acceleration of the shafts 4 of the epicyclic gear 1,2 is reduced.
    When using a gear arrangement according to FIG. 2 in a vehicle, an acceleration of the output shaft 20 due to a relief of the output shaft 20, for example a downhill, is not desirable. According to FIG. 3, provision is therefore made for braking the output shaft 20 by exerting a braking torque on the drive connection 9 with the long transmission, via a device 23 which, in the simplest case, can consist of a corresponding brake. With the deceleration of the drive connection 9, the influence of the short ratio of the drive connection 8 on the gear ratios is greater until at standstill of the drive connection 9, the short translation of the drive connection 8 exclusively for the gear ratio of the gear assembly is determining.
    However, a simple brake does not allow a sensitive reduction of the speeds of the shafts 5. In order to provide improvements here, the two shafts 5 of the epicyclic gearbox 1,2 can have, in addition to the drive connection 9, a parallel drive connection 24 with a similar, but different transmission ratio, so that the drive connections 9, 24 mutually block each other during their rigid connection through the device 23 and thereby the waves 5 are stopped. Only when allowing a slip between the gear 17 of the drive connection 9 and the gear 25 of the drive connection 24, the shafts 5 can rotate in response to the permitted slip. By corresponding matching of the devices 10 and 23, the transmission arrangement can thus be adapted to the respective requirements with regard to acceleration and braking, it being advantageous to control the devices 10 and 23 accordingly, as indicated by the arrows 26.
    4 shows a simple way of changing the direction of rotation of the output shaft 20 without a separate switching operation on the basis of a gear arrangement which basically corresponds in its construction to the gear arrangement according to FIG. 3. In contrast to Fig. 3, however, the means 10 for returning the torque of driven by the gear 19 output-side shaft 27 does not act on the shafts 4, but on the interconnected by the drive connection shafts 5. For this purpose, the shaft 27 via a Gear pair 28 drivingly connected to the device 10, which acts on the output side via a drive connection 29, the gear 17 of the drive connection 9 between the shafts 5. In addition, the means 23 for braking the drive connection 9 of the shaft 5 of the planetary gear 1 is assigned, which, however, makes no difference in terms of the basic mode of action.
    In order to further influence the rotational speed and direction of rotation of the output shaft 20, an additional three-shaft epicyclic gear 30 is provided, two of which are formed by the shaft 27 and the output shaft 20 while the third shaft 31 is separately driven the embodiment of a motor 32 which also drives the drive shaft 12 of the transmission assembly. The epicyclic gearing 30, which is also designed as a planetary gearing in the exemplary embodiment, is acted upon by a corresponding torque from the engine 32 via a drive connection 33, which torque acts on the ring gear 34, for example. The epicyclic gear 30 thus acts as summing, wherein the drive via the drive connection 33 to the drive through the shaft 27 which drives the web 35, superimposed, so that connected to the sun gear 36 output shaft 20 one of the rotational speeds and directions of rotation of the web 35 and the ring gear 34 has dependent speed and direction of rotation.
    权利要求:
    Claims (7)
    [1]
    claims
    1. gear arrangement with two identical, three shafts (3, 4, 5) having epicyclic gearboxes (1,2) between a transmission input (6) and a transmission output (7), wherein of the three pairs of corresponding shafts (3, 4, 5) of the two epicyclic gearboxes (1, 2) is assigned a pair of gears (3) to the gearbox input and output (6, 7), while the shafts (4, 5) of the two remaining pairs of gears are drivingly connected to each other in a rigid, counter-rotating gear ratio , characterized in that the two pairs of shafts of the rigidly drive-connected shafts (4, 5) have an opposite, but equal transmission ratio and that at least one of the shaft pairs of rigidly drive-connected shafts (4, 5) connected to a device (10) for torque application is.
    [2]
    2. Gear arrangement according to claim 1, characterized in that the means (10) for applying torque to the connected shaft pair (4, 5) acted upon by a braking torque.
    [3]
    3. Gear arrangement according to claim 1, characterized in that the means (10) for applying torque to the connected shaft pair (4, 5) applied to one of the shaft (12, 20) of the transmission output (7) or the transmission input (6) derived acceleration torque ,
    [4]
    4. Gear arrangement according to one of claims 1 to 3, characterized in that the means (10) for torque application to the pair of shafts of rigidly drive-connected shafts (4) is connected with a short translation.
    [5]
    5. Gear arrangement according to claim 4, characterized in that the pair of shafts of the rigidly drive-connected shafts (5) is connected to the long translation to a device (23) for applying torque with a braking torque.
    [6]
    6. Gear arrangement according to claim 5, characterized in that the means (23) for applying torque to the rigidly interconnected shafts (5) with the long translation an additional rigid drive connection (24) of these two shafts (5) with a similar, but different transmission ratio and in that one of the two shafts (5) between the two drive connections (9, 24) has a device (23) for transmitting a limited torque.
    [7]
    7. Gear arrangement according to one of claims 1 to 6, characterized in that the transmission output (7) associated with shaft (27) having a shaft of three shafts (20, 27, 31) having Umlaufrädergetriebes (30) is drivingly connected and that of the two other shafts (20, 31) of the epicyclic gearbox (1, 2) one shaft forms an output shaft (20) and the other shaft (31) can be acted on by a torque.
    类似技术:
    公开号 | 公开日 | 专利标题
    DE2525888B2|1979-04-12|Power-splitting gear arrangement
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    DE2502309A1|1975-07-24|ADJUSTABLE TWO-WAY TRANSMISSION
    DE1941445C3|1986-07-10|Synchronization switching device for a gear change transmission of motor vehicles
    DE2409914A1|1974-09-05|CONTINUOUSLY CONTROLLED TRANSMISSION
    DE102006022174A1|2007-11-15|Transmission device for distributing drive torque to two output shafts, has planetary gear sets that are provided between differential cage of differential and output of each side
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    DE102006022176A1|2007-11-15|Transmission device for distributing a drive torque to at least two output shafts
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    DE2820025B2|1980-07-24|Stepless coupling gear
    DE1164785B|1964-03-05|Epicyclic gear with hydrostatic power branch
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    DE102012009470A1|2013-11-07|Method for translated transmission of rotating movement of gear box-input shaft to gear box-output shaft in motor car, involves fixing and coupling shaft while maintaining continuous connection between gear box input- and output shafts
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    DE2246076A1|1974-03-28|UNIVERSAL, CONTINUOUSLY MECHANICAL ROTARY GEAR
    DE618015C|1935-09-02|Epicyclic gears, especially for motor vehicles
    DE102014223914B4|2016-08-25|Manual transmission device with compact design
    DE202016000743U1|2016-02-15|Continuously adjustable speed converter
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    同族专利:
    公开号 | 公开日
    WO2017041124A1|2017-03-16|
    EP3347623A1|2018-07-18|
    AT517618B1|2017-03-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE2635946A1|1975-10-10|1977-04-21|Michel Combastet|TORQUE CONVERTER|
    US4109551A|1977-01-12|1978-08-29|Nemec Allen R|Variable speed gear ratio transmission apparatus|
    DE3424421A1|1984-07-03|1986-01-09|Walter Rudolf|Gearing with mechanical power transmission for the infinitely variable adjustment of torque, speed and direction of rotation|
    GB2309272A|1996-01-19|1997-07-23|Roger James Associates|Infinitely variable ratio gearbox comprises two differential gearings in series|
    DE19960028A1|1999-12-02|2001-06-07|Frank Hoffmann|Continuous gear, e.g. for vehicle; has differential gears that can be engaged directly or indirectly, where first has main rotation and intermediate rotations that can be transmitted to second gear|
    WO2007046722A1|2005-10-18|2007-04-26|Champlon Joao Armando Soledade|Continuously variable transmission through gears|
    DE102011101887A1|2011-05-13|2012-11-15|Talip Tevkür|Method for transmitting rotary motion from input drive shaft to output driven shaft of clutchless gearbox used in motor vehicle, involves controlling speed ratio of rotational movement of coupling shaft portions|
    FR2450385B2|1979-02-28|1983-07-18|Combastet Michel|AT519361B1|2017-03-15|2018-06-15|Ing Johann Kropfreiter|transmission assembly|
    法律状态:
    2021-05-15| MM01| Lapse because of not paying annual fees|Effective date: 20200910 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50780/2015A|AT517618B1|2015-09-10|2015-09-10|transmission assembly|ATA50780/2015A| AT517618B1|2015-09-10|2015-09-10|transmission assembly|
    PCT/AT2016/050257| WO2017041124A1|2015-09-10|2016-09-09|Transmission assembly|
    EP16774447.3A| EP3347623A1|2015-09-10|2016-09-09|Transmission assembly|
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