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    • 1. 发明公开
    • GETRIEBE FÜR EIN KRAFTFAHRZEUG
    • GETRIEBEFÜREIN KRAFTFAHRZEUG
    • EP2901044A1
    • 2015-08-05
    • EP13745099.5
    • 2013-08-05
    • ZF Friedrichshafen AG
    • LUEBKE, EckhardtKALTENBACH, JohannesHUNOLD, Bernard
    • F16H37/04F16H3/00F16H3/095F16H3/097B60K6/48
    • F16H37/046B60K6/48B60K2006/4825F16H3/006F16H3/095F16H3/097F16H2200/0065F16H2200/0069F16H2200/0073F16H2200/0095
    • The present invention relates to a transmission (1), in particular a dual-clutch transmission, for a motor vehicle, comprising two sub-transmissions (2, 3), wherein each of the sub-transmissions (2,3) comprises at least one input shaft (EW1, EW2), and wherein the at least two input shafts (EW1, EW2) are arranged on a drive input side (AN) of the transmission (1) on an input shaft axis (4), comprising an output shaft, as a drive output shaft (AW) of both sub-transmissions (2, 3), on a drive output side (AB) of the transmission (1), comprising a countershaft assembly (6), and comprising a planetary gear set (GP) that is connectable to the drive output shaft (AW), wherein M gear planes (I, II, III, IV, V, VI) and N shift devices (SE1, SE2, SE3, SE3a, SE4, SE5) are provided, wherein N and M are each a natural number greater than or equal to two, wherein the countershaft assembly (6) comprises at least two countershafts (VW1 a, VW1 b) which are arranged in each case on different countershaft axes (5a, 5b), wherein the gear stages (V1, V2, V3, V4, V5, V6, V7, V8, V9, V10, V11, R1, R2, R3, R4) that can be realized by means of the M gear planes (I, II, III, IV, V, VI) and the N shift devices (SE1, SE2, SE3, SE3a, SE4, SE5) are fully powershift-capable, and wherein one of the N shift devices (SE5) is provided for the actuation of the planetary gear set (GP).
    • 本发明涉及一种用于机动车的变速器(1),特别是双离合器变速器,其包括两个子变速器(2,3),其中每个子变速器(2,3)至少包括 一个输入轴(EW1,EW2),并且其中所述至少两个输入轴(EW1,EW2)在输入轴轴线(4)上布置在变速器(1)的驱动输入侧(AN)上, 作为两个子变速器(2,3)的驱动输出轴(AW),在变速器(1)的驱动输出侧(AB)上包括中间轴组件(6),并且包括行星齿轮组 其中M个齿轮平面(I,II,III,IV,V,VI)和N个换档装置(SE1,SE2,SE3,SE3a,SE4,SE5)是可连接到驱动输出轴 其中N和M各自为大于或等于2的自然数,其中副轴组件(6)包括至少两个副轴(VW1a,VW1b),所述副轴分别设置在不同的副轴上 t轴(5a,5b),其中齿轮级(V1,V2,V3,V4,V5,V6,V7,V8,V9,V10,V11,R1,R2,R3,R4) M个齿轮平面(I,II,III,IV,V,VI)和N个换档装置(SE1,SE2,SE3,SE3a,SE4,SE5)完全具有动力换档能力,并且其中N个换档装置之一 SE5)用于驱动行星齿轮组(GP)。
    • 3. 发明公开
    • Zugkraftunterstütztes Mehrgruppengetriebe und Verfahren zu dessen Betreiben
    • ZugkraftunterstütztesMehrgruppengetriebe und Verfahren zu dessen Betreiben
    • EP2738030A2
    • 2014-06-04
    • EP13188208.6
    • 2013-10-11
    • ZF Friedrichshafen AG
    • Glueckler, Johannes
    • B60K6/48B60K6/547B60W10/06B60W10/08B60W10/111B60W20/00F16H37/04F16H3/095
    • B60K6/547B60K6/48B60K2006/4816B60W10/08B60W10/111B60W20/00B60W30/19F16H3/095F16H3/126F16H37/046F16H2200/0078F16H2200/0095Y02T10/6221Y02T10/6256Y10S903/902Y10T74/19014
    • Antriebsstrang eines Kraftfahrzeugs, mit einem einen Verbrennungsmotor (2) und eine elektrische Maschine (EM) aufweisenden Hybridantrieb und einem zwischen den Hybridantrieb und einen Achsantrieb (26) geschalteten, automatisierten Gruppengetriebe (6), wobei das automatisierte Gruppengetriebe (6) zumindest ein in Vorgelegebauweise ausgeführtes Hauptgetriebe (10) mit einer Getriebehauptwelle (22) und mindestens einer Vorgelegewelle (14, 16) sowie zumindest eine dem Hauptgetriebe (10) antriebstechnisch vorgeschaltete, insbesondere als Splitgruppe (8) ausgeführte Vorschaltgruppe aufweist, wobei die elektrische Maschine (EM) des Hybridantriebs mit der oder jeder Vorgelegewelle (14, 16) in Verbindung steht und die Vorschaltgruppe (8) und das Hauptgetriebe (10) mindestens einen gemeinsamen, schaltbaren Direktgang (G6*, G12*) durch diese beiden Getriebeteile zur zugkraftunterstützten Schaltung des Hauptgetriebes (10) aufweisen, der mit Hilfe der elektrischen Maschine (EM) schaltbar ist, wobei das Gruppengetriebe (6) eine zwischen der zumindest einen Vorschaltgruppe (8) und dem zumindest einen Hauptgetriebe (10) geschaltete Kupplung (20) zur Verbindung einer Getriebeeingangswelle (18) mit der Getriebehauptwelle (22) zur Bildung des mindestens einen Direktgangs (G6*, G12*) aufweist, wobei während der Existenz des Direktgangs (G6*, G12*) Verbindungen der Getriebeeingangswelle (18) und der Getriebehauptwelle (22) zu der oder jeder Vorgelegewelle (14, 16), sowie zur elektrischen Maschine (EM) getrennt sind..
    • 传动系具有自动组传动装置(6),其包括在分离器组(8)和主变速器(10)之间的离合器(20)。 离合器将变速器输入轴(18)连接到主变速器轴(22),以形成用于主变速器的牵引力支撑的换档的公共的可移动的直接齿轮。 在直齿轮接合的情况下,输入轴和传动轴与中间轴(14,16)和电机(EM)的连接是分开的。
    • 5. 发明公开
    • SPEED CHANGE TRANSMISSION DEVICE
    • WECHSELGETRIEBEVORRICHTUNG
    • EP1930627A1
    • 2008-06-11
    • EP06810507.1
    • 2006-09-25
    • Kubota Corporation
    • KATAYAMA, YoshiyukiUEDA, YoshihiroISHIMORI, ShosoHIRAOKA, Minoru
    • F16H3/44F16H3/091F16H47/04
    • F16H47/04F16H2037/088F16H2037/0886F16H2200/0043F16H2200/0095
    • A speed-change transmission apparatus for effecting a speed-changing on an engine drive force with utilizing a continuously variable speed-change device, a plurality of planetary transmission mechanisms and a plurality of clutches is constructed to be capable of effecting the speed-changing operation smoothly, regardless of a centrifugal force generated in the clutches.
      An output from the continuously variable speed-change device 30 and a drive force from the engine 3 are combined by a planetary transmission section P. The drive force from this planetary transmission section P is transmitted via a clutch section C to an output shaft 61. First, second, third and forth clutches 73, 74, 76, 78 of the clutch section C are configured to be switched over respectively between an engaged condition and a disengaged condition, as clutch members 75,77 are engaged with or disengaged from output side rotational members 73b, 74b, 76b, 78b.
    • 利用无级变速装置,多个行星传动机构和多个离合器来实现对发动机驱动力的变速的变速传动装置被构造成能够实现变速操作 无论离合器中产生的离心力如何,都是平稳的。 来自连续变速装置30的输出和来自发动机3的驱动力由行星传动部P组合。来自该行星传动部P的驱动力经由离合器部C传递到输出轴61。 离合器部分C的第一,第二,第三和第三和第三离合器73,74,76,78分别构造成在接合状态和分离状态之间切换,因为离合器构件75,77与输出侧接合或脱离 旋转构件73b,74b,76b,78b。
    • 8. 发明公开
    • PLANETARY GEAR TYPE TRANSMISSION
    • 行星齿轮式传动
    • EP3104039A1
    • 2016-12-14
    • EP16732893.9
    • 2016-02-01
    • Komatsu Ltd.
    • YASUTA, NobuhitoMATSUO, TakuSHIOHARA, MasakiKAMATANI, YutakaIZUMI,Kohei
    • F16H3/66
    • F16H3/66F16H2200/0065F16H2200/0086F16H2200/0095F16H2200/2012F16H2200/2046
    • A first carrier (14) rotates integrally with an input shaft (7). A third sun gear (31) and a fourth sun gear (41) rotate integrally with a first intermediate shaft (81). A third carrier (34) rotates integrally with a second ring gear (23). A fourth carrier (44) rotates integrally with a third ring gear (33), and outputs power. A first clutch (51) couples a first ring gear (13) and a second sun gear (21) to the first intermediate shaft (81), A second clutch (52) couples the first carrier (14) to a second carrier (24). A third clutch (53) couples the second carrier (24) to the first intermediate shaft (81). A first brake (61) brakes rotation of a first sun gear (11). A second brake (62) brakes rotation of the second ring gear (23) and the third carrier (34). A third brake (63) brakes rotation of a fourth ring gear (43).
    • 第一托架(14)与输入轴(7)一体旋转。 第三太阳轮(31)和第四太阳轮(41)与第一中间轴(81)一体旋转。 第三行星架(34)与第二齿圈(23)一体旋转。 第四行星齿轮架(44)与第三齿圈(33)一体旋转并输出动力。 第一离合器51将第一齿圈13和第二太阳齿轮21连接到第一中间轴81.第二离合器52将第一行星架14连接到第二行星架24 )。 第三离合器(53)将第二行星架(24)联接到第一中间轴(81)。 第一制动器(61)制动第一太阳轮(11)的旋转。 第二制动器(62)制动第二环形齿轮(23)和第三行星架(34)的旋转。 第三制动器(63)制动第四环形齿轮(43)的旋转。
    • 9. 发明公开
    • FAHRZEUGGETRIEBE
    • EP2971854A1
    • 2016-01-20
    • EP14705097.5
    • 2014-02-12
    • ZF Friedrichshafen AG
    • KALTENBACH, JohannesZIEMER, PeterBORNTRAEGER, Kai
    • F16H3/66F16H3/00
    • F16H3/66F16H3/006F16H2003/442F16H2003/445F16H2200/006F16H2200/0078F16H2200/0086F16H2200/0095F16H2200/201F16H2200/2012F16H2200/2015F16H2200/2053F16H2200/2056F16H2200/2058F16H2200/2061F16H2200/2094F16H2200/2097
    • The invention relates to a vehicle transmission comprising two transmission input shafts (GE1, GE2) and at least three planet gear sets (PG1, PG2, PG3), each transmission input shaft (GE1, GE2) being associated with a partial transmission (TG1, TG2). One of the two partial transmissions (TG1, TG2) comprises at least the first planet gear set (PG1) and the other partial transmission of the two partial transmissions (TG1, TG2) comprises at least the second planet gear set (PG2). The aim of the invention is to provide a vehicle transmission that can be cost-effectively produced and can be used both in conventional and hybrid powertrains. According to the invention, the transmission input shafts (GE1, GE2) are or can be operatively connected to the planet gear sets (PG1, PG2, PG3) such that the two partial transmissions (TG1, TG2) can be variably activated to provide a plurality of gear ratios, and one of the gears can be shifted as a direct gear.
    • 本发明涉及一种车辆变速器,包括两个变速器输入轴(GE1,GE2)和至少三个行星齿轮组(PG1,PG2,PG3),每个变速器输入轴(GE1,GE2)与一个局部传输相关联(TG1, TG2)。 一两个变速器部分(TG1,TG2)的包括至少所述第一行星齿轮组(PG1)以及两个变速器部分(TG1,TG2)的另一部分传输包括至少所述第二行星齿轮组(PG2)。 本发明的目的是提供一种车辆变速器,该车辆变速器可以经济有效地制造并且可以用于传统动力传动系和混合动力传动系中。 根据本发明,变速器输入轴(GE1,GE2)是或可以可操作地连接到行星齿轮组(PG1,PG2,PG3),使得两个分变速器(TG1,TG2)可以被可变地激活以提供 多个齿轮比,并且其中一个齿轮可以作为直接档位移动。
    • 10. 发明公开
    • TWIN CLUTCH TYPE TRANSMISSION
    • 双离合器式变速箱
    • EP2578901A1
    • 2013-04-10
    • EP11789777.7
    • 2011-05-31
    • Hitachi Nico Transmission Co., Ltd.
    • IBAMOTO, MasahikoNAKAMURA, HidekiHAGIHARA, Daisuke
    • F16H3/093
    • F16H3/08F16H3/006F16H2037/044F16H2037/049F16H2200/006F16H2200/0095Y10T74/19233
    • A twin clutch transmission for a large horsepower vehicle having a compact size and a high transmission efficiency is obtained.
      In a twin clutch transmission, there are provided an input shaft, an odd-numbered level speed change mechanism 30, an even-numbered level speed change mechanism 60, a synchronizing speed change mechanism 100, and an output mechanism 90. The speed change mechanisms 30 and 60 include transmission gear trains 32 and 62, main clutches 34 and 64 for selectively transmitting the powers of the transmission gear trains 32 and 62 to the transmission shafts 40 and 70. The synchronizing speed change mechanism 100 includes synchronizing gear trains 110 and 120 for coupling the rotation of the odd-numbered level transmission shaft 32 with the rotation of the even-numbered level transmission shaft 62, and synchronizing clutches 112 and 122 for selecting coupling by this synchronizing gear train.
    • 获得了具有紧凑尺寸和高传动效率的用于大马力车辆的双离合器变速器。 在双离合器变速器中,设置有输入轴,奇数级变速机构30,偶数级变速机构60,同步变速机构100和输出机构90.变速机构 30和60包括传动齿轮系32和62,用于选择性地将传动齿轮系32和62的动力传递到传动轴40和70的主离合器34和64.同步变速机构100包括同步齿轮系110和120 用于将奇数级传动轴32的旋转与偶数级传动轴62的旋转连接,并使同步齿轮系选择连接的离合器112和122同步。