CN1313935A - 非同轴式输出的变速器 - Google Patents

非同轴式输出的变速器 Download PDF

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CN1313935A
CN1313935A CN99809901A CN99809901A CN1313935A CN 1313935 A CN1313935 A CN 1313935A CN 99809901 A CN99809901 A CN 99809901A CN 99809901 A CN99809901 A CN 99809901A CN 1313935 A CN1313935 A CN 1313935A
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gear
transmission
shaft
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output shaft
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CN1123713C (zh
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赫伯特·霍伊尔
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ZF Friedrichshafen AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/12—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with means for synchronisation not incorporated in the clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/091—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears including a single countershaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
    • F16H37/043—Combinations of toothed gearings only change gear transmissions in group arrangement without gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/12—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with means for synchronisation not incorporated in the clutches
    • F16H2003/123—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with means for synchronisation not incorporated in the clutches using a brake
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • General Details Of Gearings (AREA)
  • Motor Power Transmission Devices (AREA)

Abstract

本发明涉及一种汽车变速器(6、60),包括输入轴(32、64)、主轴(38、66)、中间轴(46、86)和输出轴(112),它们设置为可绕旋转轴线(114、116)旋转,以及包括一些活动地(68、70、72、74、96、98、111、128)和固定地(76、78、80、88、90、92、94、108、110、130)装在这些轴(32、38、46、60、64、66、112、132)上的齿轮。在输出轴(112)上传扭地装一个齿轮(110、111、128),它由一个与中间轴(86)传扭连接的齿轮(108、130)传动,这一齿轮对(108－110、108－111、130－128)构成一个常数速比。变速器(60)的输入轴(64)与主轴(66)传扭连接,输入轴(64)的旋转轴线(116)与主轴(66)的旋转轴线(116)构成同一条轴线。主轴(66)的旋转轴线(116)与输出轴(112)的旋转轴线(114)不构成同一条轴线,以及,主轴(66)和输出轴(112)的旋转轴线(114、116)彼此之间的距离(118)由常数速比的齿轮对(108－110、108－111、130－128)的传动比决定。

Description

非同轴式输出的变速器
本发明涉及一种按权利要求1前序部分所述有主轴和中间轴的变速器。
由先有技术已知具有输入轴、主轴、中间轴和输出轴的变速器，其中，输入轴、主轴和输出轴位于公共的旋转轴线上。这种类型的变速器可有整体式的输入轴和主轴或整体式的主轴和输出轴。例如在DE19538192中说明了这种类型的变速器。
根据要求的变速器传动比，确定轴的齿轮上的齿数。这就决定了平行轴的齿轮彼此的直径比，并因而也确定了平行轴相互的空间距离。例如，通常由主轴上的第一个齿轮和在中间轴上从输入侧看去的第一个齿轮组成的齿轮对设计为，为在中间轴上直径很大的齿轮配设一个在输入轴上直径很小的齿轮。这一齿轮对允许以低的转速水平传递大的扭矩。但是大的空间距离造成大的变速箱尺寸，从而可能导致在汽车制造中安装空间方面的困难。
本发明的目的是减小变速器安装空间的需求以及减小变速器的尺寸。
此目的通过具有权利要求1特征的变速器达到。从属权利要求说明了一些设计。
按本发明建议，在变速器的输出轴上传扭地装一个齿轮，它由一个与中间轴传扭连接的齿轮传动，这一齿轮对构成一个常数。变速器的输入轴与主轴传扭连接。输入轴的旋转轴线和主轴的旋转轴线构成同一条轴线，而主轴的旋转轴线和输出轴的旋转轴线不构成同一条轴线。主轴与输出轴的旋转轴线彼此之间的距离取决于常数速比齿轮对的传动比。
按一种有利的设计，常数速比的齿轮对装在分开的变速箱内，以便能更换齿轮对。
按另一项有利的设计，设置用于传动液体动力车辆减速器的附加输出轴，它可直接由主轴或中间轴传动，以便在没有增速传动级作为中间连接的情况下获得高的车辆减速器转速。
一项有利的设计涉及在输出轴上二级变速器(Splitgetriebe)的换档装置，用于将变速器档位分为变速器半档速度比的间隔。
按一项有利的设计，设形式上的行星齿轮变速器的区域副变速器，它与常数速比的齿轮对连接，用于扩展变速器的总工作范围。
通过将变速器的一个常数速比的配置移至变速器输出侧端部以及主轴与输出轴旋转轴线的非同轴性，达到减小变速器大齿轮直径的目的。因此，直径减小可以降低齿轮重量以及减小平行轴的轴间距，从而导致减小变速器的结构尺寸。变速器结构尺寸减小意味着在此部位有利地降低了重量和在汽车内有更大的安装空间。与此同时，较小的齿轮和机箱所需要的材料消耗量和加工工作量的减少导致降低成本。要运动的以及在换档时要同步的齿轮质量较小，导致换档力明显低于已知的传统变速器的换档力。同理，由于要同步的质量较小，所以同步装置也可以减小。
由于在输入轴或主轴与中间轴之间小的轴间距而在中间轴输入侧端部的齿轮较小，所以中间轴的转速较高。因此变速器的绝大部分扭矩较小，变速器的构件必须依据此扭矩进行设计。只有在常数速比的输出装置中由于在输出轴与中间轴之间存在增大的轴间距才形成更大的扭矩。对于具有山区行车排档和高速档方案的变速器结构，采用本发明的配置，变速器输入扭矩可以设计成同样大小。
由于输入轴和主轴的整体式结构，所以可以取消按先有技术主轴轴颈在输入轴内的支承。设在变速器端部的齿轮对可以设计为在通常的变速箱下游的一个单独的结构组合件，并因而可以实现在常数速比的输出装置处有不同齿轮对的变速器模块式结构方式。
下面借助于附图进一步说明本发明。其中：
图1按先有技术的变速器；
图2按本发明的变速器结构示意图；以及
图3按图2具有二级变速器的结构。
图1用放大图表示一种按先有技术的变速器6，在这里例如包括五个前进档和一个倒车档。用一根换档杆18作用在三根换档滑杆20、22和24上，它们通过换档拨叉将同步装置26、28和30运动到要求的接通位置。例如同步装置30接通倒车档和第一个变速器速比。同步装置26接通变速器档位2和3，而同步装置28用于接通变速器档位4和5。变速器输入轴32通过支承装置，例如在这里所画的轴承36支承在变速箱34内。主轴38通过轴承40支承在变速器输入轴32内以及通过支承装置，例如在这里所画的轴承42支承在变速箱34内。用于倒车档的转向的改变通过惰轮44实现，它的齿与主轴38上的倒车档齿轮的齿以及与中间轴46的齿啮合。在主轴38上用于前进档传动比的其他一些齿轮的齿，同样与中间轴46上相应的齿啮合。此外，在变速器输入轴32上还设有用于安装离合器54的齿。
图2表示按本发明的变速器结构示意图。变速器60有变速箱62，输入轴64***此箱内。输入轴64与变速器60的主轴66设计成一体。在主轴66上装有七个齿轮68、70、72、74、76、78、80，其中齿轮68、70、72、74可活动地在主轴66上旋转，而齿轮76、78、80始终与主轴66传扭连接。在齿轮68与70之间设一同步装置82，按选择可使齿轮68或齿轮70与主轴66传扭连接。在齿轮72与74之间设同步装置84，按选择可使齿轮72或齿轮74与主轴66传扭连接。
在中间轴86上同样设有七个齿轮88、90、92、94、96、98、100，其中齿轮88、90、92、94始终与中间轴86传扭连接。在齿轮96与98之间设一同步装置102，按选择可使齿轮96或齿轮98与中间轴86传扭连接。为了倒车档所需的旋转反向，齿轮100与惰轮104啮合，而惰轮104又与主轴66上的齿轮80啮合。齿轮98与附加输出轴122上的齿轮120啮合，附加输出轴122传动车辆减速器。由于齿轮98的直径大，所以附加输出轴122被传动为具有高的转速。
在这里所画的图中，设另一个机箱106与变速箱62连接。在机箱106内装有一个由两个齿轮108和110组成的齿轮对，其中齿轮108与中间轴86传扭连接。齿轮110始终与输出轴112传扭连接。但齿轮108和110也可以装在相应设计的变速箱62中。
齿轮110和输出轴112绕一条想象的旋转轴线114旋转。主轴66和装在主轴上的一些齿轮以及输入轴64绕一条旋转轴线116旋转。这两条旋转轴线114和116互相并不处于同轴位置，而是通过一个轴间距118彼此分开。
图3表示了一种结构，与图2相比它通过在机箱106内的二级变速器扩展了工作范围，以构成第二个常数速比。在这里，在输出轴112上设同步装置126，按选择齿轮111或齿轮128可与输出轴传扭连接。齿轮108与齿轮130一起传扭地装在轴132上。

Claims (5)

1．汽车变速器(6、60)，包括输入轴(32、64)、主轴(38、66)、中间轴(46、86)和输出轴(112)，它们设置为可绕旋转轴线(114、116)旋转，以及包括一些活动地(68、70、72、74、96、98、111、128)和固定地(76、78、80、88、90、92、94、108、110、130)装在这些轴(32、38、46、60、64、66、112、132)上的齿轮，其特征为：在输出轴(112)上传扭地装一个齿轮(110、111、128)，它由一个与中间轴(86)传扭连接的齿轮(108、130)传动，这一齿轮对(108-110、108-111、130-128)构成一个常数速比；变速器(60)的输入轴(64)与主轴(66)传扭连接，输入轴(64)的旋转轴线(116)与主轴(66)的旋转轴线(116)构成同一条轴线；以及，主轴(66)的旋转轴线(116)与输出轴(112)的旋转轴线(114)不构成同一条轴线，主轴(66)和输出轴(112)的旋转轴线(114、116)彼此之间的距离(118)由常数速比的齿轮对(108-110、108-111、130-128)的传动比决定。
2．按照权利要求1所述的汽车变速器(6、60)，其特征为：常数的齿轮对(108-110、108-111、130-128)装在分开的变速器箱(106)内，以便能更换齿轮对(108-110、108-111、130-128)。
3．按照权利要求1或2所述的汽车变速器(6、60)，其特征为：设置用于传动液体动力车辆减速器(124)的附加输出轴(122)，它可直接由主轴(66)或中间轴(86)传动，以便在没有增速传动级作为中间连接的情况下获得高的车辆减速器(124)转速。
4．按照权利要求1至3之一所述的汽车变速器(6、60)，其特征为：在输出轴(112)上设二级变速器(134)的同步装置(126)，用于将变速器档位分为变速器半档速度比的间隔。
5．按照权利要求1至3之一所述的汽车变速器(6、60)，其特征为：设形式上为行星齿轮变速器的区域副变速器，它与常数速比的齿轮对(108-110、108-111、130-128)连接，用于扩展变速器(60)的总工作范围。
CN99809901A 1998-08-20 1999-08-14 非同轴式输出的变速器 Expired - Fee Related CN1123713C (zh)

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CN101449170B (zh) * 2006-05-19 2011-05-11 Zf腓德烈斯哈芬股份公司 用于获知变速器主轴转速的方法和具有转速测量装置的变速器
CN1987150B (zh) * 2005-12-21 2011-07-27 现代自动车株式会社 六速手动传动装置
CN102470829A (zh) * 2009-07-01 2012-05-23 Zf腓德烈斯哈芬股份公司 带有液力减速器的机动车变速箱

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DE19950048A1 (de) * 1999-10-16 2001-04-19 Zahnradfabrik Friedrichshafen Stufenautomatgetriebe für ein Kraftfahrzeug
DE10134054A1 (de) * 2001-07-13 2003-01-23 Zahnradfabrik Friedrichshafen Fahrzeuggetriebe
RU2259282C2 (ru) * 2003-07-25 2005-08-27 Темираев Руслан Казбекович Гидравлико-инерционный преобразователь, система управления им, коробка перемены передач и способ преобразования ими крутящего момента
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DE102006002968A1 (de) * 2006-01-21 2007-08-16 Zf Friedrichshafen Ag Zahnräderwechselgetriebe mit einem nachgeschalteten, konstant übersetzten Zusatzantrieb
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KR100619316B1 (ko) 2006-09-05
KR20010072677A (ko) 2001-07-31
JP2002523697A (ja) 2002-07-30
BR9913090A (pt) 2001-05-08
EP1104515A1 (de) 2001-06-06
WO2000011373A1 (de) 2000-03-02
EP1104515B1 (de) 2003-07-09
DE59906268D1 (de) 2003-08-14
DE19837776A1 (de) 2000-02-24
CN1123713C (zh) 2003-10-08
JP4330801B2 (ja) 2009-09-16

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