• 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 five-shaft planetary gearbox (1), comprising at least one web (7) connected to a web shaft (2) with a planetary gearset (8) consisting of a first planetary gear (9), which is connected to a first sun gear shaft (9). 3) connected to the first ring gear (12) is meshed with a first ring gear (5) and a second planet gear (10) connected to a second sun gear (4) second sun gear (13 ) and a second ring gear (14) connected to a second ring gear (6) is in meshing engagement, wherein in each case a first planet gear (9) and a second planet gear (10) on a web (7) of the web shaft (2) rotatably supported with each other and wherein the first sun gear shaft (3), the second sun gear shaft (4), the land shaft (2) and the first ring gear shaft (5) at least predominantly on a first side (17) of a normal plane (ε) on a central axis of rotation (1a ) and the second ring gear (6) on a second side (18) of the normal plane (ε) are arranged. The second sun gear (13) and the second ring gear (14) are arranged on different sides (17, 18) of the normal plane (ε).
    公开号:AT514323A4
    申请号:T50844/2013
    申请日:2013-12-20
    公开日:2014-12-15
    发明作者:Stefan Lichtenegger
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    1 56738
    The invention relates to a five-shaft planetary gear, with at least one web connected to a web with a planetary gear consisting of a first planetary gear which is in mesh with a first sun gear connected to a first sun gear and a first ring gear connected to a first ring gear and a second planetary gear meshing with a second sun gear connected to a second sun gear shaft and a second ring gear connected to a second ring gear, wherein a first planet gear and a second planet gear are rotatably supported to mesh with each other on a land of the land shaft, and wherein the first sun gear, the second sun gear, the land and the first ring gear are disposed at least predominantly on a first side of a normal plane to a central axis of rotation and the second ring gear on a second side of the normal plane. Furthermore, the invention relates to a drive train with a five-shaft planetary gear.
    From DE 199 09 424 Al a hybrid transmission for vehicles, consisting of a drive shaft, an output shaft, a continuously variable actuating gear and a mechanical overlay and gearbox is known. The superposition gear is a five-shaft planetary gear with a ridge shaft as the transmission output shaft. The bridge carries several sets of intermeshing planets. The planets mesh with two ring gears and two sun gears. The two sun gears are connected to each other via a stepless control gear. A first ring gear is firmly connected to an internal combustion engine, a second ring gear via a brake to the transmission housing. Except for a Hohlradwelle all waves of the five-shaft planetary gear are arranged on the output side. First ring gear and first sun gear are arranged on one side, second ring gear and second sun gear on the other end face of the planetary gear.
    DE 103 03 894 B4 describes a power shift transmission for motor vehicles, consisting of a planetary and a stepped transmission. The planetary gear has five shafts, namely a drive shaft, two reaction shafts and a slow coupling shaft, and a fast coupling shaft, each reaction shaft is detectable with one housing brake and the drive shaft and a reaction shaft with a clutch are switchable and wherein the coupling shafts as drive shafts are provided for multi-step transmission. The 2/16 2
    Planetary gear has planetary gear sets, each with three planetary gears meshing with each other. Two of the five shafts - the two ring gear shafts - are arranged on one side, the other three shafts on the other side.
    DE 37 13 106 Al discloses a multi-speed change gear for motor vehicles with two juxtaposed three-shaft planetary gears, which have a common web shaft. In this case, two shafts of this double-three-shaft planetary gear - namely a ring gear and a ridge wave - arranged on one side and the other four waves on the other side.
    The object of the invention is to achieve a high functionality in a transmission of the type mentioned with little effort and space.
    According to the invention this is achieved in that the second sun gear and the second ring gear are arranged on different sides of the normal plane, wherein preferably the second sun gear on the first side and the second ring gear on the second side of the normal plane are arranged.
    A particularly compact arrangement can be realized if the normal plane represents a center plane of the five-shaft planetary gear, wherein preferably the components of the first sun gear, first ring gear, first planetary gear and second planetary gear are arranged symmetrically with respect to the normal plane.
    Only a few components are required if the - measured in the axial direction - width of the second planetary gears is greater than the width of the first planetary gears, the second planet gears are arranged with respect to the first planet gears on both sides of the normal plane and the outstanding areas of the Form second gears first and second tooth meshing zones. The space can be kept very small, if the second sun gear is at least a second planetary gear in the first meshing zone and the second ring gear with at least one second planetary gear in the second meshing zone in meshing engagement.
    By extending at least one second planetary gears in the axial direction, it is possible to interchange the position of a central wheel with respect to the web shaft with respect to a second central gear. As central wheels sun gears and ring gears are called. In comparison to known five-shaft planetary gears thus a changed order of the waves is possible, whereby new transmission structures can be realized.
    The five-shaft planetary gear is particularly well suited for a powertrain, in particular for a hybrid vehicle, wherein an element of the five-shaft planetary gear - selected from the group web, first sun gear, second sun gear, first ring gear, second ring gear -, preferably the Web, via at least one clutch with a preferably formed by an internal combustion engine first drive machine is drive-connected.
    Another element of the five-shaft planetary gear, preferably the first ring gear may be connected to a second drive machine preferably formed by an electric machine. Furthermore, another element of the five-shaft planetary gear, preferably the second ring gear, be connected to an output shaft.
    It is particularly advantageous if a further element of the five-shaft planetary gear, preferably the first sun gear, can be drive-connected to the first drive machine via at least one further clutch, wherein the first drive machine preferably has a first element between a first drive machine and five-shaft drives Planetary gear arranged three-shaft planetary gear -selected from the group Sonnerad, web,
    Ring gear - and the first sun gear shaft is connected via the further coupling with a second element of the three-shaft transmission or connectable, wherein particularly preferably a third element of the three-shaft planetary gear is blocked.
    Preferably, a further element of the five-shaft planetary gear, preferably the second sun gear, formed blockable via a braking device.
    With the drive train having the five-shaft planetary gear various operating modes can be realized. In particular, in at least one steplessly power-split operating range, a main clutch-preferably a first or the second clutch device-is activated and at least one clutch and / or brake element from the group brake device, first clutch or second in at least one Gangstufenbetriebsbereich Coupling - preferably also another element of this group - are activated.
    In a first steplessly power-split operating range, the main clutch and the second clutch device, and in a second steplessly power-split operating range, the main clutch and the first clutch can be activated. Preferably, in the continuously power-split operating range, the first drive machine and the second drive machine are activated, wherein in particular the first drive machine stationary, and the second drive machine is operated by a motor or generator.
    In at least one gear stage operating range, the first drive machine can be transient and the second drive machine can be operated by motor or generator. A purely electrical operation is possible if in at least one gear stage operating range of the primary drive is deactivated and the secondary drive is operated by a motor or generator.
    In a first gear stage operating range, the brake device, preferably also the second clutch device, is activated. In a second gear stage operating range, the first clutch, preferably also the second clutch device, activated, activated in a third gear stage operating range, the first clutch and the braking device.
    Thus, there are a total of eight modes of operation, namely two hybrid modes of operation with stepless power split, three hybrid modes of operation with fixed ratios, and three purely electrical modes of operation.
    The invention will be explained in more detail below with reference to FIG.
    It show schematically
    1 shows a five-shaft planetary gear according to the invention,
    2 shows the five-shaft planetary gear in a section along the line II -II in Fig.l, 5/16. 5
    3 shows a drive train with this five-shaft planetary gear,
    Fig. 4 is a speed-ladder diagram of this drive train and
    Fig. 5 is a switching matrix of this drive train.
    The five-shaft planetary gear 1 shown in FIGS. 1 and 2 has a land shaft 2, a first sun gear shaft 3, a second sun gear shaft 4, a first ring gear shaft 5, and a second ring gear shaft 6.
    The web shaft 2 is connected to at least one web 7, wherein on each web 7, a planetary gear set 8 with a first and a second planetary gear 9, 10 is arranged. The two planetary gears 9, 10, whose axes 9a, 10a are spaced from each other, are meshed with each other.
    The five-shaft gearbox 1 may have a plurality, for example three, about the circumference uniformly distributed planetary gear sets 8 with first and second planetary gears 9, 10.
    The first sun gear shaft 3 is connected to a first sun gear 11, which meshes with the first planet gear 9 in meshing engagement. The first planetary gear 9 is further in meshing engagement with a first ring gear 12 connected to the first ring gear shaft 5.
    Furthermore, the second sun gear 4 with a second sun gear 13 and the second ring gear 6 with a second ring gear 14 are connected.
    Reference symbol ε denotes a normal plane, designed as a center plane of the five-shaft planetary gear 1, on the central axis of rotation la. The normal plane ε also forms the plane of symmetry for the components of the first sun gear 11, the first ring gear 12, the first planetary gear 9 and the second planetary gear 10.
    Measured in the direction of the central axis of rotation la, the width B of the second planetary gear 10 is greater than the width b of the first planetary gear. 9
    With respect to the first planetary gear 9, the second planetary gear 10 is superposed on both sides of the normal plane ε, with the towering 6/16 6
    Form regions of the second planetary gear 10 first and second tooth engagement zones 15, 16 for the second sun gear 13 and for the second ring gear 14. The width of the protruding areas is designated by reference a. The second sun gear 13 and the second ring gear 14 are arranged on different sides with respect to the normal plane ε, wherein the second sun gear 13, the first sun gear 3, a second sun gear 4, the first ring gear 5, and - at least predominantly - the web shaft 2, on a first side 17 and the second ring gear 14, and the second ring gear 6 are arranged on a second side 18.
    FIG. 3 shows a drive train 20, for example for a hybrid vehicle, in which the five-shaft planetary gear 1 illustrated in FIG. 1 is installed.
    In this case, the web 7 or the web shaft 2 of the five-shaft planetary gear 1 with the drive shaft 21 of a first drive machine 22, such as an internal combustion engine, via switchable clutches - main clutch CO and first clutch CI - connectable. The first ring gear shaft 5 of the five-shaft planetary gear 1 is connected to a second drive machine 23, which is formed in the embodiment by an electric machine. The second ring gear 6 is - possibly via a transfer case VG and / or a differential D- connected to at least one output shaft 24, 25, 26 of the drive train 20. The first sun gear shaft 3 of the five-shaft planetary gear 1 can be drive-connected to the first drive machine via at least one further second clutch C2. The first drive machine 22 with a first element 31, for example, with a ring gear, and the first sun gear 3 via the second clutch C2 with a second element 32, for example with a web, arranged between the first drive machine 22 and five-shaft planetary gear three Shaft planetary gear 30 is connected or connectable, wherein particularly preferably a third element 33, for example, a sun gear, the three-shaft planetary gear 30 blocked, for example, is connected to a transmission housing 27. The second sun gear 4 of the five-shaft planetary gear 1 can be blocked via a brake device Bl.
    With the drive train shown in FIG. 3, in addition to a continuously power-split first operating range evl, a steplessly power-split second operating range ev2 can be realized, as is shown in FIG
    Fig. 4 shown speed ladder diagram and the switching matrix shown in Fig. 5 shows.
    FIG. 4 shows the possible operating modes of the drive train 20 shown in FIG. 3 on the basis of a ladder diagram for the rotational speeds n with the drive rotational speed n 1 of the first drive machine 22.
    By activating the second clutch C2 and the brake device Bl, or the first and second clutches CI, C2 or the second clutch CI and the brake device Bl, three forward gears gl, g2, g3 can be switched.
    The main clutch CO is used to uncouple the first drive machine 22 and is only deactivated here if the drive is taken over exclusively by the second drive machine 23 or no drive takes place. In the neutral position N, all clutches CO, CI, C2, as well as the braking device Bl are deactivated.
    The operating ranges evl and ev2 represent steplessly power-split operating ranges. In the operating range ev2, the first main clutch CO and the first clutch CI are activated, in the first operating range evl, on the other hand, the main clutch CO and the second clutch C2 are activated. In the operating areas evl and ev2, the second drive machine 21 formed, for example, by an electric machine can be operated by a motor or by a generator. 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.
    Fig. 5 shows a switching matrix of the clutches CO, CI, C2 and the braking device Bl for the operating modes shown in Fig. 3, where " X " represents the activated state of the corresponding clutches CO, CI, C2 or braking device Bl. Here, the operating modes (gear stages) el, e2 and e3 for pure drive by the second drive machine 23 - apart from the position 8/16 8 of the main clutch CO - equivalent to the operating modes (gear stages) gl, g2 and g3 for combined drive and can be both forward and reverse gears. 9/16
    权利要求:
    Claims (14)
    [1]
    9 PATENT CLAIMS 1. Five-shaft planetary gear (1), with at least one web (7) connected to a web shaft (2) with a planetary gear set (8) consisting of a first planetary gear (9), which with one with a first sun gear ( 3) connected to the first ring gear (12) is meshed with a first ring gear (5) and a second planet gear (10) connected to a second sun gear (4) second sun gear (13 ) and a second ring gear (14) connected to a second ring gear (6) is in meshing engagement, wherein in each case a first planet gear (9) and a second planet gear (10) on a web (7) of the web shaft (2) rotatably supported with each other are, and wherein the first sun gear (3), the second sun gear (4), the web shaft (2) and the first ring gear (5) at least predominantly on a first side (17) of a normal plane (ε) on a central axis of rotation (la ) and d The second ring gear (6) on a second side (18) of the normal plane (ε) are arranged, characterized in that the second sun gear (13) and the second ring gear (14) on different sides (17, 18) of the normal plane (ε ) are arranged. 2. Five-shaft planetary gear (1) according to claim 1, characterized in that the second sun gear (13) on the first side (17) and the second ring gear (14) on the second side (18) of the normal plane (ε) are arranged. 3. Five-shaft planetary gear (1) according to claim 1 or 2, characterized in that the normal plane (ε) represents a center plane of the five-shaft planetary gear (1), wherein preferably the elements first sun gear (11), the first ring gear (12), the first planetary gear (9) and the second planetary gear (10) are arranged symmetrically with respect to the normal plane (ε). 4. Five-shaft planetary gear (1) according to one of claims 1 to 3, characterized in that - measured in the axial direction - width (B) of the second planet gear (10) is greater than the width (b) of the first 10th Planetary gear (9), wherein the second planet gear (10) with respect to the first planet gear (9) on both sides (17, 18) of the normal plane (ε) are outstanding and the projecting portions of the second planet gear (10) form first and second tooth engagement zones (15, 16). 5. Five-shaft planetary gear (1) according to claim 4, characterized in that at least one second planet gear (10) in the first tooth engagement zone (15) with the second sun gear (13) and in the second tooth engagement zone (16) with the second Ring gear (14) is in meshing engagement.
    [2]
    6. powertrain (20), in particular for a hybrid vehicle, with a five-shaft planetary gear (1) according to one of claims 1 to 5, characterized in that an element of the five-shaft planetary gear (1) -selected from the group Web (7), first sun gear (11), second sun gear (13), first ring gear (12), second ring gear (14) - preferably the web (7), via at least one clutch (C0; CI), with a preferably through an internal combustion engine formed first drive machine (22) is drive-connected.
    [3]
    7. Drive train (20) according to claim 6, characterized in that a further element of the five-shaft planetary gear, preferably the first ring gear, is connected to a preferably formed by an electric machine second drive machine.
    [4]
    8. Drive train (20) according to claim 6 or 7, characterized in that a further element of the five-shaft planetary gear, preferably the second ring gear, is connected to at least one output shaft.
    [5]
    9. Drive train (20) according to any one of claims 6 to 8, characterized in that a further element of the five-shaft planetary gear (1), preferably the first sun gear (11) via at least one further clutch (C2) with the first Drive machine (22) is drive-connected, wherein preferably the first drive machine (22) with a first element of between the first drive machine (22) and the five-shaft planetary gear (1) arranged three-shaft planetary gear (30) - selected from the group Sun wheel (33), web (32), ring gear (33) - and the first sun gear (11) via the further clutch 11/16 11 (C2) connected to a second element of the three-shaft planetary gear (30) or connectable is particularly preferably, a third element of the three-shaft planetary gear (20) is blocked.
    [6]
    10. The drive train (20) according to any one of claims 6 to 9, characterized in that a further element of the five-shaft planetary gear (1), preferably the second sun gear (13), via a braking device (Bl) is blockable.
    [7]
    11. A method for operating a drive train (20) according to one of claims 6 to 10, characterized in that in at least one continuously power-split operating range (evl, ev2) a main clutch (C0) - preferably also a first (CI) or the second clutch device (C2) - is activated, and that in at least one gear stage operating range (gl, g2, g3, el, e2, e3) at least one clutch and / or brake element from the group brake device (Bl), first clutch (CI) or second clutch (C2) - preferably also another element of this group - is activated.
    [8]
    12. The method according to any one of claims 11, characterized in that in a first continuously power-split operating range (evl), the main clutch (C0) and the second clutch means (C2), and in a second steplessly power-split operating range (ev2), the main clutch (CO) and the first clutch (CI) are activated.
    [9]
    13. The method according to claim 11 or 12, characterized in that in the continuously power-split operating range (evl, ev2) the first drive machine (22) and the second drive machine (23) are activated, wherein preferably the first drive machine (22) stationary, and second drive machine (23) is operated by a motor or generator.
    [10]
    14. The method according to any one of claims 11 to 13, characterized in that in at least one gear stage operating range (GL, G2, G3), the first drive machine (22) is operated transiently and the second drive machine (23) is operated by a motor or generator. 12/16 12
    [11]
    15. The method according to any one of claims 11 to 14, 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.
    [12]
    16. The method according to any one of claims 11 to 15, characterized in that in a first gear stage operating range (gl; el), the braking device (Bl), preferably also the second clutch device (C2), is activated.
    [13]
    17. The method according to any one of claims 11 to 16, characterized in that in a second gear stage operating range (g2; e2), the first clutch (CI), preferably also the second clutch device (C2) is activated.
    [14]
    18. The method according to any one of claims 11 to 17, characterized in that in a third gear stage operating range (gl; el), the first clutch (CI) and the braking device (Bl) are activated. 2013 12 20 feet / hour 13/16
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    同族专利:
    公开号 | 公开日
    AT514323B1|2014-12-15|
    WO2015091317A1|2015-06-25|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    CN102267368A|2011-04-29|2011-12-07|北京工业大学|Transmission mechanism for power coupling|EP3100888A1|2015-06-03|2016-12-07|ZF Friedrichshafen AG|Transmission for a motor vehicle, and power train for a hybrid vehicle having such a transmission|AT384092B|1986-04-22|1987-09-25|Steyr Daimler Puch Ag|MULTI-SPEED INTERCHANGEABLE GEARBOX FOR MOTOR VEHICLES|
    DE19909424A1|1999-02-23|2000-08-24|Peter Tenberge|Hybrid gearing for vehicle|
    EP1279543B1|2001-07-23|2006-11-29|Nissan Motor Co., Ltd.|Hybrid drivetrain for a vehicle|
    DE10303894B4|2003-01-30|2005-02-03|Technische Universität Chemnitz|power shift|
    US8366580B2|2010-10-05|2013-02-05|GM Global Technology Operations LLC|Transmission having at least ten speeds|DK3379109T3|2017-03-23|2021-08-30|Cascade Drives Ab|COMBINED PLANET GEAR DEVICE AND GEAR DEVICE|
    AT520219B1|2017-09-12|2019-02-15|Avl List Gmbh|Torque transmission device, drive system and motor vehicle|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50844/2013A|AT514323B1|2013-12-20|2013-12-20|Five-shaft planetary transmission|ATA50844/2013A| AT514323B1|2013-12-20|2013-12-20|Five-shaft planetary transmission|
    PCT/EP2014/077682| WO2015091317A1|2013-12-20|2014-12-15|Five-shaft planetary gearing|
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