• 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 a transmission (1) comprising a drive train having a prime mover with a primary drive shaft (16), in particular for a vehicle, having a Ravigneaux planetary gear set (2) with one two sun gear shafts (10, 13), one land shaft (18) and at least one Hohlradwelle (12) having double planetary gear, and an upstream, designed as a reduction gear simple planetary gear set (3) with the gear elements sun gear (5a), web (8a) and ring gear (6a), wherein a first of the gear elements deseinfachen planetary gear set (2), in particular the sun gear (5a) is fixed to the housing. In order to achieve high functionality with little effort and space requirement, it is provided that at least a first element of the Ravigneaux planetary gearset (2), preferably permanently, is drive-connected to a secondary drive (21), which is preferably formed by an electrical machine.
    公开号:AT513538A1
    申请号:T50310/2013
    申请日:2013-05-08
    公开日:2014-05-15
    发明作者:
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    1 56609
    The invention relates to a transmission with a primary drive having a primary drive shaft having drive train, in particular for a vehicle, with a Ravigneaux planetary gear set with a two Sonnenradwellen, a bridge shaft and at least one Hohlradwelle having double planetary gear, and an upstream, designed as a reduction gear simple planetary gear set the gear elements sun gear, web and ring gear, wherein a first of the transmission elements of the simple planetary gear set is fixed to the housing. Furthermore, the invention relates to a method for operating the transmission.
    A transmission of the type mentioned is known from US 5,106,352 A. Such so-called Lepelletier gearboxes are used for example in automatic transmissions of vehicles and represent a further development of the so-called Ravigneaux set - a double planetary gear - is.
    The Lepelletier set is created by a Ravigneaux set preceded by another simple planetary gear set and connected with couplings. The ring gear of the simple planetary gear set is permanently connected to the motor drive shaft. This means that even at idle the simple planetary gear is always rotated. The output takes place via the ring gear of the Ravigneaux set and is connected via the differential with the drive wheels. The sun gear of the simple planetary gearset is permanently blocked. The disadvantage is that a large number of clutches and brakes, as well as for starting separate starting devices, such as hydrodynamic torque converter or the like, are required.
    DE 10 2004 053 044 A1 discloses a transmission for a hybrid drive with a double planetary gear set and a simple planetary gear set, each sun gear shaft of the double planetary gearset being drive-connected to one electric machine each.
    The object of the invention is to avoid the disadvantages mentioned and to achieve high functionality in a transmission of the type mentioned with little effort and space.
    According to the invention this is achieved in that at least a first element of the Ravigneaux planetary gear set, preferably permanently, with a 2/20 2
    Secondary drive is drive connected. The secondary drive can be advantageously formed by an electric machine. This makes it possible to combine primary drive and secondary drive in an advantageous manner or alternatively to use.
    Preferably, a second element of the Ravigneaux planetary gear set can be blocked by means of a braking device.
    It is particularly advantageous if a third element of the Ravigneaux planetary gearset, preferably a first sun gear shaft of the Ravigneaux planetary gearset, is particularly preferably permanently connected to a second gear element of the simple planetary gearset, preferably to the web of the simple planetary gear train.
    The first element of the Ravigneaux planetary gear set can be formed by a second sun gear shaft and the second element by the web shaft. Alternatively, it may be provided that the first element are formed by the ridge wave of the Ravigneaux planetary gear set and the second element by the second sun gear shaft of the Ravigneaux planetary gearset. Thus, the positions of the secondary drive and the braking device within the Ravigneaux planetary gear set to achieve special requirements in terms of space requirements and functional requirements can be exchanged advantageous.
    The first sun gear shaft and the second sun gear shaft have different directions of rotation, since the first sun gear shaft acts on a set of second planet gears via a set of first planet gears, whereas the second sun gear shaft acts directly on the set of second planet gears.
    A further alternative variant according to the invention provides that the first element of the Ravigneaux planetary gear set is formed by a second ring gear. The secondary drive may be indirectly connected via a transmission stage or directly connected to the second ring gear. This embodiment has the advantage that a second continuously power-split operating range can be realized.
    The simple planetary gearset forms a reduction gear and is preferably designed as a negative gear. Minus transmissions are planetary gearboxes in which - with 3/20 3 of a retained shaft - the two other shafts rotate in different directions of rotation.
    In this case, at least one element of the Ravigneaux planetary gear set, preferably the web shaft, can be drive-connected to the primary drive - for example, an internal combustion engine, in particular via a first clutch device. The same element of the Ravigneaux planetary gear set can alternatively, preferably permanently, be drive-connected to a drive machine formed for example by an electric machine.
    A very compact design can be achieved if the Ravigneaux planetary gear set and / or the simple planetary gear set is disposed within a rotor of the primary secondary drive.
    On the one hand to enable a stepless power-split operating range and on the other hand three speed ratios for combined drive and purely electric drive, the transmission requires only a single braking device for blocking a sun gear of the Ravigneaux planetary gear set and three coupling devices. In this case, a first coupling device between the primary drive shaft and a transmission input shaft is arranged. According to a preferred embodiment of the invention, a second coupling device between the two sun gear shafts of the Ravigneaux planetary gear set and a third clutch device between the gear input shaft and the ridge shaft of the Ravigneaux planetary gearset can be arranged.
    In a first embodiment of the invention, in the continuously power-split operating range, only the first clutch device is activated -also closed-while the other clutch devices, as well as the brake device deactivated - ie open - are. In other embodiments according to the invention, the first clutch device and the second or the third clutch device are activated in at least one continuously power-split operating range. In an embodiment variant in which the secondary drive acts on the Ravigneaux planetary gear set via a second ring gear, the first and the second clutch device and in a second steplessly 4/20 4 power-split operating range are the first clutch device and the third clutch device activated.
    In the infinitely power-driven operating range, the primary drive can be operated stationary or the secondary drive as a generator or motor. In continuous power-split startup, current can be generated at startup - up to a certain limit speed. Furthermore, a continuous electrodynamic starting is possible. A separate starting element, such as a hydrodynamic torque converter, can be omitted. The first clutch device has only separation or Zuschaltfunktion and does not serve as a starting clutch.
    In at least one gear stage operating range, the brake device, the second clutch device or the third clutch device are activated.
    In an alternative particularly advantageous embodiment of the invention, the second coupling device is not between the two Sonnenradwellen the Ravigneaux planetary set, but between a first sun gear of the Ravigneaux planetary gear set and a sum shaft of the simple planetary gear set, in particular the web arranged. Thus, by separating the drive connection between the first sun gear of the Ravigneaux planetary gear set and the land of the simple planetary gearset, the sum shaft can be made torque-free. The first and third coupling device can be positioned the same, as in the previously described embodiment variant. In each gear stage region, apart from the first clutch device, two elements from the group of second clutch device, third clutch device and brake device are activated and the third element is deactivated. This allows a comparatively large spread in the individual gear stage areas. Furthermore, the efficiency of the transmission is improved.
    The changeover from the continuously split-power operating range to one of the three speed ranges (gears) can be done during the ferry operation. During operation in one of the three shiftable gears, the secondary operation can optionally be operated as a generator or as a motor to provide hybrid functionality such as " boost " (Supporting the drive torque of the prime mover), " recuperation ", " load point shift " 5/20 5 or " Sailing " perform. In all gears an electromotive torque application can take place. During the Rekuperierens a very high efficiency can be achieved because between the output and the electric machine little losses (only idling losses) occur.
    In comparison to known Lepelletier transmissions results in a significant reduction in clutch and brake devices.
    The invention will be explained in more detail below with reference to FIG.
    2 shows a speed-ladder diagram of this transmission, FIG. 3 shows a switching matrix of this transmission, FIG. 4 shows a transmission according to the invention in a second embodiment, FIG. 5 shows a speed-ladder diagram 7 shows a transmission according to the invention in a third embodiment, FIG. 8 shows a transmission according to the invention in a fourth embodiment, FIG. 9 shows a speed-ladder diagram of this transmission, FIG. 10 shows a shifting matrix of this transmission and FIG. 11 shows a transmission according to the invention in a fifth embodiment variant.
    Functionally identical parts are provided in the embodiments with the same reference numerals.
    The transmission 1 has in all variants in each case a Ravigneaux planetary gear set 2 with an upstream simple planetary gearset 3, wherein the simple planetary gear set 3 is designed as a Reduzierplanetensatz formed by a negative gear.
    The Ravigneaux planetary gearset 2 formed essentially by a double planetary gearset has a first and a second sun gear 10a, 13a which are connected to corresponding first and second sun gear shafts 10, 13 and at least one first ring gear 12a connected to a ring gear shaft 12.
    A set of first planetary gears 18a mesh with the first ring gear 12a and the second sun gear 13a. A set of second planetary gears 18b mesh with the first sun gear 10a and mesh with the first planetary gears 18a. 6/20 6
    In the embodiments according to FIGS. 8 and 11, the Ravigneaux planetary gearset 2 has a second ring gear 22a, which meshes with the planetary gears 18b in meshing engagement.
    The simple planetary gearset 3 has in all embodiments a permanently coupled to the housing 4 of the transmission 1 first differential shaft 5 of the sun gear 5a. The second differential shaft 6 of the ring gear 6a of the simple planetary gear set 2 is permanently rotatably connected to the transmission input shaft 7. The sum shaft 8 of the web 8a of the simple planetary gear set 3 is permanently connected to the first sun gear shaft 10 of the Ravigneaux planetary gear set 2 via a first gear shaft 9. The output is via a transmission output shaft 11, which is permanently rotatably connected to a ring gear 12 of the Ravigneaux planetary gear set 2 in combination. The second sun gear shaft 13 of the Ravigneaux planetary gear set 2 is rotatably connected to a second transmission shaft 14 in connection. The first and second transmission shafts 9, 14, and the Getriebeantriebs- and output shafts 7, 11 may be designed as a coaxially formed central shafts.
    The transmission input shaft 7 can be drive-connected via a first clutch device 15 and a primary drive shaft 16 with a not shown primary drive. The prime mover may be, for example, an internal combustion engine.
    In the first embodiment variant shown in FIG. 1, a second coupling device 17 is provided between the first and second transmission shaft 9, 14, which makes it possible to connect the two sun gear shafts 10, 13 of the Ravigneaux planetary gear set 2.
    In contrast, in the second embodiment shown in Fig. 4, instead, the second coupling means 17a between the first gear shaft 9 and the sum shaft 8 of the web 8a of the simple planetary gear set 3, via which the rotary connection between the web 8a of the simple planetary gear set 3 and the first sun gear 10a of the Ravigneaux planetary gear set 2 can be interrupted. The sum wave 8 (ridge wave) of the simple planetary gear set 3 can thus be switched torque-free by the second clutch device 17a. 7/20 7
    The ridge shaft 18 of the Ravigneaux planetary gear set 2 can be rotatably connected to the transmission input shaft 7 via a third clutch device 19 in all three variants. Furthermore, the second sun gear shaft 13 of the Ravigneaux planetary gear set 2 or the second gear shaft 14 can be blocked by a brake device 20.
    The rotor of the secondary drive 21 formed by an electrical machine is permanently connected to the ridge shaft 18 of the Ravigneaux planetary gear set 2.
    FIG. 2 shows the possible operating modes of the transmission 1 shown in FIG. 1 on the basis of a ladder diagram for the rotational speeds n with the input rotational speed n 1 of the primary drive.
    By activating the second or third clutch device 17, 19 or the brake device 20, three forward gears gl, g2, g3 can be switched. The first coupling device 15 is used to disconnect the prime mover and is only deactivated when the drive is taken over exclusively by the secondary drive 21 or no drive.
    If none of the clutch or brake devices 17, 19, 20 is activated, the drive train can be operated in a continuously power-split operating range by advantageously operating the primary drive stationarily and the secondary drive 21 is operated in a first operating range bl as a generator and in a second operating range b 2 as a motor becomes. As a result, a continuous electrodynamic starting is possible, whereby a separate starting element such as a hydrodynamic torque converter or a starting clutch can be omitted. The switchover from the continuously split-mode operation into one of the three shiftable gears gl, g2, g3 can take place while driving. During operation in one of the three switchable speeds g1, g2, g3, the secondary mode 21 can optionally be operated as a generator or as a motor to perform hybrid functionalities such as " boost ", recuperation " " load point shift " or " sailing " to enable.
    FIG. 3 shows a switching matrix of the coupling devices 15, 17, 19 and the braking device 20 for the operating modes shown in FIG. 2, wherein a " X " the activated state of the corresponding coupling devices 15, 17, 19 or 8/20 8
    Braking device 20 represents. Here, the operating modes (gear steps) el, e2 and e3 for pure drive by the prime mover 21 - apart from the position first clutch means 15 - equivalent to the operating modes (gear stages) gl, g2 and g3 for combined drive and both forward, as also be reverse gears.
    FIG. 5 shows the possible operating modes of the transmission 1 shown in FIG. 4 on the basis of a ladder diagram for the rotational speeds n with the input rotational speed n 1 of the primary drive.
    By activating the second clutch device 17a and the brake device 20, or the second and third clutch device 17a, 19, or the third clutch device 19 and the brake device 20, three forward gears gl, g2, g3 can be switched. The first coupling device 15 is used for decoupling the primary drive and is only deactivated here if the drive is taken over exclusively by the drive machine 21 or no drive takes place.
    If none of the coupling or braking devices 17a, 19, 20 is activated, the drive train can also be operated in a continuously power-split operating range in the second embodiment variant by virtue of the primary drive being operated stationary and the drive machine 21 being regenerated in a first operating region bl a second operating range b2 is operated by a motor. As a result, a continuous electrodynamic starting is possible, whereby a separate starting element such as a hydrodynamic torque converter or a starting clutch can be omitted. The switchover from the continuously split-mode operation into one of the three shiftable gears gl, g2, g3 can take place while driving. During operation in one of the three switchable speeds gl, g2, g3, the secondary drive 21 can optionally be operated as a generator or as a motor to perform hybrid functions such as " boost ", recuperation " " load point shift " or " sailing " to enable.
    From the illustrated in Fig. 5 speed ladder diagram for the second embodiment is clear that by the arrangement of the second clutch 17a between the web 8a of the simple planetary gear set 3 and the first sun gear 10a of the Ravigneaux planetary gear set 2 compared to the first 9 / 20 9
    Embodiment variant, a greater spread in the individual gear stage areas gl, g2, g3; el, e2, e3 becomes possible. Further, the load shiftability can be improved because in the gear stage regions g1, g2, g3; el, e2, e3 only one coupling / braking device 15, 17a, 19, 20 must be superimposed. In addition, an improvement in efficiency can be achieved because of the four switching elements - clutch devices 15, 17a, 19 and braking device 20 - three in the internal combustion engine gear stages gl, g2, g3 and two in the electrical gear stages el, e2, e3 are activated (closed) as is apparent from the switching matrix of the coupling devices 15, 17a, 19 and the braking device 20 shown in FIG. 6 for the embodiment variant shown in FIG. 5, the states of the coupling devices 15, 17a, 19 and the braking device 20 are entered, wherein a " X " represents the activated state of the corresponding coupling devices 15, 17a, 19 or braking device 20. The operating modes (gear stages) el, e2 and e3 for pure drive by the engine 21 are - in addition to the first clutch means 15 - again equivalent to the operating modes (gear stages) gl, g2 and g3 for combined drive and both forward, and Be reverse gears.
    The positions of the secondary drive 21 and the brake device 20 in the Ravigneaux planetary gear set 2 can also be reversed, for example, to improve spatial constraints or functional specifications. The transmission 1 shown in FIG. 7 differs from the embodiment shown in FIG. 4 in that the brake 20 acts on the carrier shaft 18 and the secondary drive 21 (via the second transmission shaft 14) on the sun gear shaft 13.
    Furthermore, it is also possible for the secondary drive 21 via another element-for example, a second ring gear 22a-to act on the Ravigneaux planetary gearset 2, as shown in FIGS. 8 and 11. The second ring gear 22a may be engaged with the second planetary gears 18b. Fig. 8 shows an embodiment in which the secondary drive 21 is drive-connected directly to the second ring gear 22a. In Fig. 11, another example is shown, in which the secondary drive 21 is indirectly connected via a transmission stage 23 and a ring gear 22 with the second ring gear 22a. 10/20 10
    These embodiments have the advantage that, in addition to a steplessly power-split first operating range evl, a steplessly power-split second operating range ev2 can be realized, as can be seen from the speed-conductor diagram shown in FIG. 9 and the switching matrix shown in FIG. FIGS. 9 and 10 differ from FIGS. 5 and 6 primarily by the additional operating range ev2, in which the first clutch 15 and the third clutch 19 are activated. in the first operating range evl, however, the first clutch 15 and the second clutch 17a are activated analogously to the operating range b1 / b2 from FIGS. 5 and 6. As in the operating range bl / b2, the secondary drive 21, which is formed for example by an electric machine 21, can also be operated by motor or generator in the operating ranges evl and ev2.
    The terms " primary " and " secondary " in primary and secondary drive are used here evaluation free and only to distinguish the drives. Both the primary drive, as well as the secondary drive can be designed as a main or predominantly used standard or main drive for the vehicle, the respective other drive can be designed as a temporary switchable auxiliary drive. It is equally possible to carry out both drives equally and - possibly alternately - to use both as a standard or main drive, as well as an auxiliary drive. Furthermore, a common equivalent use of the two drives in the switching ranges gl, g2, g3 is possible. 11/20
    权利要求:
    Claims (20)
    [1]
    11 CLAIMS 1. gearbox (1) having a drive train having a prime mover with a primary drive shaft (16), in particular for a vehicle, with a Ravigneaux planetary gear set (2) having a two Sonnenradwellen (10, 13), a ridge shaft (18) and at least one ring gear (12) having double planetary gear, and an upstream, designed as a reduction gear simple planetary gear set (3) with the transmission elements sun gear (5a), web (8a) and ring gear (6a), wherein a first of the transmission elements of the simple planetary gear set (2 ), in particular the sun gear (5a), is fixed to the housing, characterized in that at least a first element of the Ravigneaux planetary gearset (2), preferably permanently, is drivingly connected to a secondary drive (21), which is preferably formed by an electric machine.
    [2]
    2. Transmission (1) according to claim 1, characterized in that a second element of the Ravigneaux planetary gear set (2) by means of a braking device (20) is blockable.
    [3]
    3. Transmission (1) according to claim 1 or 2, characterized in that a third element of the Ravigneaux planetary gear set (2), preferably a first sun gear (10) of the Ravigneaux planetary gear set (2), - particularly preferably permanently - with a second Transmission element of the simple planetary gear set (3), preferably with the web (8a) of the simple planetary gear set (3), drivingly connected or by means of a second coupling means (17a) is drive-connected.
    [4]
    4. Transmission (1) according to one of claims 1 to 3, characterized in that the first element by a second sun gear (13) or the web shaft (18) of the Ravigneaux planetary gear set (2) and the second element by the web shaft (18 ) or the second sun gear (13) of the Ravigneaux planetary gear set (2) are formed.
    [5]
    5. Transmission (1) according to one of claims 1 to 3, characterized in that the first element of the Ravigneaux planetary gear set (2) by a second ring gear (22a) is formed. 12/20 12
    [6]
    6. transmission (1) according to one of claims 1 to 5, characterized in that at least one element of the Ravigneaux planetary gear set (2), preferably the first element of the Ravigneaux planetary gear set (2), particularly preferably the web shaft (18) of Ravigneaux -Planetensatzes (2), with the - preferably by an internal combustion engine formed - prime mover is drive-connected.
    [7]
    7. Transmission (1) according to one of claims 1 to 6, characterized in that the simple planetary gear set (3) is designed as a reduction gear and / or as a minus gear.
    [8]
    8. transmission (1) according to one of claims 1 to 7, characterized in that the Ravigneaux planetary gear set (2) and / or the simple planetary gear set (3) within a rotor of the prime mover or the secondary drive (21) is arranged.
    [9]
    9. transmission (1) according to one of claims 1 to 8, characterized in that the primary drive shaft (16) and a transmission input shaft (7) by means of a first coupling means (15) are drehverbindbar.
    [10]
    10. Transmission (1) according to one of claims 1 to 9, characterized in that the two sun gear shafts (10, 13) of the Ravigneaux planetary gear set (2) by means of a second coupling device (17) are drehverbindbar.
    [11]
    11. Transmission (1) according to one of claims 1 to 10, characterized in that the gear drive shaft (7) and the web shaft (18) of the Ravigneaux planetary gear set (2) by means of a third coupling means (19) are drehverbindbar.
    [12]
    12. A method for operating a transmission (1) according to one of claims 9 to 11, characterized in that in at least one continuously power-split operating range (bl, b2), the first coupling means (15) - preferably also the second (17a) or the third Coupling device (19) - is activated, and that in at least one gear stage operating range (gl, g2, g3, el, e2, e3) at least one first device from the group braking device (20), second 13/20 13 coupling device (17, 17a) or third coupling means (19) - preferably also a further device of this group - is activated.
    [13]
    13. The method according to any one of claims 12, characterized in that in a first continuously power-split operating range (evl) the first clutch means (15) and the second clutch means (17a), and in a second steplessly power-split operating range (ev2) the first clutch means (evl) 15) and the third coupling means (19) are activated.
    [14]
    14. The method according to claim 12 or 13, characterized in that in the continuously power-split operating range (bl, b2) of the prime mover and the secondary drive (21) are activated, preferably the stationary drive stationary, and the secondary drive (21) is operated by a motor or generator ,
    [15]
    15. The method according to any one of claims 12 to 14, characterized in that in at least one gear stage operating range (GL, G2, G3), the prime mover is operated transiently and the secondary drive (21) is operated by a motor or generator.
    [16]
    16. The method according to any one of claims 12 to 15, characterized in that in at least one gear stage operating range (el, e2, e3) of the primary drive is deactivated and the secondary drive (21) is operated by a motor or generator.
    [17]
    17. The method according to any one of claims 12 to 16, characterized in that in a first gear stage operating range (gl; el), the braking device (20), preferably also the second coupling device (17a) is activated.
    [18]
    18. The method according to any one of claims 12 to 17, characterized in that in a second gear stage operating range (g2; e2), the third clutch means (19), preferably also the second clutch means (17a) is activated. 14/20 14
    [19]
    19. The method according to any one of claims 12 to 18, characterized in that in a third gear stage operating range (g3, e3), the second coupling means (17) is activated.
    [20]
    20. The method according to any one of claims 12 to 18, characterized in that in a third gear stage operating range (gl; el), the third clutch device (19) and the braking device (20) are activated. 2013 05 08 Fu 15/20
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    同族专利:
    公开号 | 公开日
    CN104936808A|2015-09-23|
    US9644715B2|2017-05-09|
    EP2909051B1|2017-08-02|
    JP2015535205A|2015-12-10|
    WO2014063980A1|2014-05-01|
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    CN104936808B|2018-01-23|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50464/2012A|AT512912B1|2012-10-22|2012-10-22|transmission|
    ATA50310/2013A|AT513538B1|2012-10-22|2013-05-08|transmission|ATA50310/2013A| AT513538B1|2012-10-22|2013-05-08|transmission|
    JP2015538377A| JP2015535205A|2012-10-22|2013-10-17|Transmission and operating method thereof|
    PCT/EP2013/071681| WO2014063980A1|2012-10-22|2013-10-17|Transmission and a method for operating same|
    CN201380055361.XA| CN104936808B|2012-10-22|2013-10-17|Speed changer and the method for operating the speed changer|
    EP13780112.2A| EP2909051B1|2012-10-22|2013-10-17|Transmission and method for operating the same|
    KR1020157013408A| KR20150079728A|2012-10-22|2013-10-17|Transmission and a method for operating same|
    US14/437,361| US9644715B2|2012-10-22|2013-10-17|Transmission and a method for operating same|
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