CN101617146B - 无级变速传动装置 - Google Patents

无级变速传动装置 Download PDF

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CN101617146B
CN101617146B CN2008800056033A CN200880005603A CN101617146B CN 101617146 B CN101617146 B CN 101617146B CN 2008800056033 A CN2008800056033 A CN 2008800056033A CN 200880005603 A CN200880005603 A CN 200880005603A CN 101617146 B CN101617146 B CN 101617146B
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gear
transmission
transmission device
speed changer
output terminal
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菲利普·邓肯·温特
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Torotrak Development Ltd
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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
    • 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
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • 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
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H37/086—CVT using two coaxial friction members cooperating with at least one intermediate friction member
    • 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • 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
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • 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
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft

Abstract

一种无级变速传动装置，具有传动装置输入端(60)和传动装置输出端(114)。传动装置具有变速器(56)。变速器是以无级变速比传输驱动力的装置。它还包括一包含离合装置(152)的周转齿轮装置(58)。周转齿轮装置具有三个旋转部件。旋转部件之一接合至具有至少一个行星齿轮(94)的行星架(86)。另一旋转部件接合至与行星齿轮啮合的主齿轮(90)。离合装置将剩余的旋转部件接合至均与行星齿轮啮合并以不同速度旋转的第一和第二可选择齿轮(96、98)中任一个。前述旋转部件之一以固定传动比接合至传动装置输入端。旋转部件之一接合至变速器输出端。最后一个旋转部件接合至传动装置输出端。传动装置通过离合装置可在第一和第二比率范围之间变化。

Description

无级变速传动装置
技术领域
本发明涉及无级变速传动装置(continuously variabletransmission)(“CVT”)，且更具体地，涉及使用周转分路器齿轮传动装置(epicyclic shunt gearing)的CVT。
背景技术
在图1中高度示意性地示出了本领域技术人员众所周知的这样一种CVT。发动机10驱动传动装置输入轴12。传动装置输出轴14接合至机动车辆的车轮16。传动比的无级变速由变速器(variator)18提供。本文将使用的词“变速器”是指一种以无级变速比在第一旋转部件(例如变速器输入轴20)与第二旋转部件(例如输出轴22)之间传输动力的装置。传动装置还包括一具有三根轴的周转分路器齿轮系24(其结构未在本图中示出)。分路器的第一轴26可操作地接合至发动机10，例如，通过固定比率的齿轮传动装置接合。分路器的轴28接合至变速器18的输出轴22。第三轴30以第一轴和第二轴速度的函数的速度旋转，并接合至传动装置输出轴14。
该类型的传动装置可提供无限减速，在本领域中称之为“齿轮空档(geared neutral)”。在某变速比(variator ratio)上，分路器24的第一旋转轴26和第二旋转轴28的速度相互抵消，使第三轴30以及传动装置输出端静止，尽管实际上输出端并没有从运转的发动机上物理地分离。通常，选择传动装置中的齿轮齿数比以便仅通过改变变速比就能使由传动装置整体上提供的速比在包括齿轮空档的倒档(reverse gear)和前进档(forward gear)的范围内变化。
由分路器24通过变速器18使动力(power，功率)沿与从发动机至车轮的动力流动相反的方向再循环(或反之亦然，在发动机制动期间)。这种动力再循环减少了通过变速器的总动力流(powerflow)，从而要求变速器仅传输由传动装置所传输的总动力的一部分。通常，变速器是传动装置的能量效率最低的部分。因此希望将流过它的动力降至最小。
现在，在一些具有传统分级传动比主变速箱的机动车辆中，在主变速箱与车轮之间设置有副变速箱。拖拉机通常具有这种类型的设置。对于例如耕作的低速操作，副变速箱置于低比率中。当需要较高速度，例如当在道路上行驶时，副变速箱置于高比率中。副变速箱同样可与CVT一起使用。在图1中，这样的变速箱在32处以虚线显示，并可在低范围与高范围之间转换。
优化这种CVT的效率遇到了一个问题。假定低范围旨在提供从倒车15kph至前进15kph的车速，并且高范围旨在提供直到40kph的前进速度。很明显，在图1所示的设置类型中，这可通过为副变速箱32选择合适的传动比来实现。在高范围内，传动装置将因而能够提供从前进40kph至倒车40kph的车速。但是，大多数情况下并不需要这么高的倒车速度，并且这种系统的变速效率将不是最理想的。由变速器传输的总动力的比例随着传动比范围的增大而变大。因此，在图1的传动装置中，在高范围内，变速器传输了没必要那么大的动力比例，从而降低了传动装置的效率。
发明内容
根据本发明，其提供了一种无级变速传动装置，包括传动装置输入端、传动装置输出端、适于以无级变速比在变速器输入端与变速器输出端之间传递驱动力的变速器、以及包括离合装置的周转齿轮装置(epicyclic gear arrangement)，周转齿轮装置具有三个旋转部件，旋转部件中的一个接合至承载至少一个行星齿轮的行星架，旋转部件中的一个接合至与行星齿轮啮合的主齿轮，并且将离合装置设置成将剩余的旋转部件接合至第一和第二可选齿轮中的任一个，该第一和第二可选齿轮均与行星齿轮啮合并以不同速度旋转，旋转部件中的一个以固定传动比接合至传动装置输入端，旋转部件中的一个接合至变速器输出端，并且旋转部件中的一个接合至传动装置输出端，从而通过离合装置，传动装置可在第一和第二比率范围之间变化。
例如，旋转部件可以采用轴的形式，但是它们的功能在于将旋转驱动力传输给周转齿轮(epicyclic gear)的相关部件或传输来自周转齿轮相关部件的旋转驱动力，因此可能使用能够做到这一点的任何部件。例如，在下面将描述的传动装置中，变速器输出盘通过多根杆或轴直接接合至行星架，并且这些杆或轴形成相应的旋转部件。这里的“接合(coupling，联接)”是指在指定部件之间具有用于传输驱动力的路径，并且这可能利用一个部件至另一个部件的直接物理连接，或者可能利用齿轮传动装置或诸如链传动的其他合适的机械装置。
附图说明
现在将参照附图，仅以实例的方式，描述本发明的具体实施例，附图中：
图1是动力再循环类型的CVT的示意图；
图2为体现本发明的传动装置的简化图示；
图3为图2中示出的传动装置的透视图；以及
图4为体现本发明的第二传动装置的简化图示。
具体实施方式
在图2和图3示出的传动装置中，发动机50通过包括变速器56和周转分路器58的CVT54接合至车轮52。
发动机50可为内燃机。图示的传动装置尤其适于与限速(speedgoverned)的柴油机一起使用，例如，常见于诸如拖拉机的农用车辆以及建筑业中所用的车辆。在具有发动机和传动装置的这种组合的车辆中，驾驶员可设定一个选定的发动机转速，然后通过调节变速比执行对车速的控制。至少在低速情况下，驾驶员可通过此方式在前进速度和倒车速度的连续范围中进行选择，并且可通过选择齿轮空档使车辆停住。但是，应注意，根据本发明的这些CVT不仅适于与限速的发动机一起使用，而且可以与任何合适的旋转驱动器(例如电动机、外燃机等)一起使用。轴60将发动机接合至变速器输入端，并形成传动装置的输入轴。当然，实际上在发动机与变速器之间可插设齿轮传动装置。
示例中的变速器56属于环形滚道滚动牵引型(toroidal racerolling traction type)。更具体地说，其属于本领域中公知的“全环形”。这种变速器是众所周知的，在此将仅作简单描述。可利用包括(但不限于)带轮变速器(belt and sheave variators)和液力变速器(hydrostatic variators)在内的其他类型的变速器实施本发明。
图示的变速器56具有第一输入滚道62和第二输入滚道64，在它们之间为单个输出滚道74。输入滚道62、64分别具有朝向形成在输出滚道74的相对侧上的类似形状的轨道(raceway)70、72的半环形凹入式轨道66、68。输入滚道62、64以及输出滚道74被安装成围绕由轴75所限定的一个公共轴旋转，在此实例中，轴75仅为传动装置输入轴60的延伸部分。输入和输出滚道共同限定出两个基本上为环形的腔76、78，每个腔各包括一组相应的辊子80、82。这些辊子在轨道上滚动，从而在外滚道62、64(它们被接合成共同转动)与内滚道74之间传输动力。这些辊子被安装成围绕它们自身的轴线转动，在84处示出了其中一根轴线，图中可看出其向轴75倾斜。这些辊子的倾斜角度是可变的，并与变速器的传动比相对应。改变辊子的倾斜度就会改变辊子在滚道上运行路径的周长，从而改变内滚道的速度相对于外滚道的速度的比率，即其改变了变速器的传动比。
变速器56的输入侧由发动机50以固定比率驱动(应注意的是，虽然，便利的是参考由发动机驱动传动装置和车轮的情况，但是在“滑行(over-run)”或“发动机制动”的情况下动力流当然也可沿其他方向)。在图示的实施例中，发动机驱动轴60、75，并且第一输入滚道62安装于轴75上以随其旋转。轴75延伸穿过全部滚道并伸出于第二输入滚道64的外侧，在第二输入滚道的外侧，轴75承载有行星架86。行星架通过轴88接合至第二输入滚道的外表面，从而使第二输入滚道64可随轴75一起旋转。
变速器的输出侧接合至主齿轮90。在图示的实施例中，通过与轴75同轴并围绕轴75设置的套筒92而实现此接合，该套筒从输出滚道74穿过第二输入滚道64延伸至第二输入滚道的外侧区域。第二输入滚道64与套筒92之间的轴承允许一个相对于另一个旋转。行星架86的轴88承载与主齿轮90啮合的行星齿轮组94。行星齿轮组94不但能够绕它们自身的轴旋转，而且可以绕周转轮系的轴在圆轨道内运行。
行星齿轮组还与第一和第二可选输出齿轮96、98啮合。在图2的实施例中，可看到行星齿轮组具有分别与主齿轮90以及第一和第二输出齿轮96、98啮合的三个独立的齿轮头(toothed gear head)100、102、104。这种结构允许单独地选择行星齿轮组94借以与其他齿轮啮合的齿的数量，以提供所需的比率，但是在其他实施例中，行星齿轮组中的每一齿轮可能各有一套能够与全部三个相关联的齿轮90、96、98啮合的轮齿。例如，为了制造和组装方便，实际上，行星齿轮组94也可形成为多重接合部件(multiple coupledcomponent)。行星齿轮组94以不同的速度驱动两个输出齿轮96、98。在图示的实施例中，这是由于第一输出齿轮96比第二输出齿轮98小，而与其啮合的齿轮头102相应地比对应的齿轮头104大。两个输出齿轮在任何时候都由行星齿轮组94驱动，并且其中之一通常接合至传动装置的输出端，进而通过离合装置106接合至车轮52。
在图2和图3中，离合装置自身使用一种输出周转齿轮装置108，以使该装置能够与轴75同轴。第一输出齿轮96通过轴112接合至离合器110的一部分。离合器110的另一部分接合至传动装置输出轴114。在离合器的一种状态下，离合器因而将第一输出齿轮96接合至传动装置输出轴114。围绕轴112而设置的套筒111用来将第二输出齿轮98接合至周转齿轮108的太阳齿轮116，该周转齿轮的行星架118接合至离合器110的又一部分。输出周转齿轮还具有固定的内齿轮120。在离合器的另一种状态下，离合器因而用来通过输出周转齿轮108将传动装置输出轴114接合至第二输出齿轮98。切换离合器的状态，从而在高和低范围之间变化。
重要的是应认识到，图2和图3示出的实施例在功能上并不等同于图1中所示的传动装置。两个都能够提供高传动比和低传动比范围。但是，图1中的副变速箱32仅能通过某一因素(当然，该因素在两个范围内不同)增加从其周转齿轮系24输出的速度。从而如上所述，低范围可能提供从倒车15kph至前进15kph的车速，而高范围可能提供从倒车40kph至前进40kph的车速。总范围在齿轮空档任一侧的比例无法在低范围与高范围之间改变。图2和图3的传动装置并不涉及同样的限制。因此，例如可选择齿轮齿数比以在低范围内提供从-15kph至+15kph的车速，而在高范围内提供从-15kph至+40kph的车速。由于在高范围内分布的总比率较小，在仍然提供所需的最大前进速度时，通过变速器的总传输动力的比例可变小，从而传动装置可以更加高效。
图4中示出的传动装置在很多方面都与图2和图3中示出的传动装置类似，并且相应部件给出了相同的附图标号(虽然仅主要部件以这种方式标示)，但是取代输出周转齿轮108，图4的方案具有这样的设置：其采用偏移于轴75的副轴150。副轴齿轮152、154分别与两个输出齿轮96、98的齿轮头啮合，并与副轴同轴，但能够绕其旋转。离合器152用于选择性地将副轴齿轮152、154中的一个接合至副轴，从而将该齿轮的旋转传至车轮52。
在不脱离本发明范围的情况下，对图示的实施例进行许多可能的发展和变型都是可行的。例如，周转齿轮传动装置通常在行星齿轮组的外侧设置一个内齿轮，并且这样的设置可应用于体现本发明的传动装置中，例如，采用与行星齿轮组上的相应齿轮头啮合的两个独立的内齿轮来代替输出齿轮96、98。

Claims (1)

1.一种无级变速传动装置，包括：传动装置输入端；传动装置输出端；变速器，所述变速器适于以无级变速比在变速器输入端与变速器输出端之间传输动力；以及包括离合装置的周转齿轮装置，所述周转齿轮装置包括：
承载至少一个行星齿轮的行星架，所述行星架接合至所述变速器输入端，
接合至所述变速器输出端的主齿轮，以及
所述行星齿轮通过第一齿轮头而与所述主齿轮啮合，
其中，所述行星架包括两个其它齿轮头，所述两个其它齿轮头分别与第一和第二输出齿轮啮合，所述离合装置适于选择性地通过将所述第一输出齿轮接合至所述传动装置输出端而进行第一传动范围或者通过将所述第二输出齿轮接合至所述传动装置输出端而进行第二传动范围，
所述传动装置的特征在于，齿轮传动装置设置成使得所述第一传动范围和所述第二传动范围均提供所述传动装置输出端的正转和倒转，其中具有第一齿轮空档变速比，当所述传动装置处于第一范围中时，所述第一齿轮空档变速比使得所述传动装置输出端静止，并且具有第二齿轮空档变速比，当所述传动装置处于第二范围中时，所述第二齿轮空档变速比使得所述传动装置输出端静止，并且所述第一齿轮空档变速比与所述第二齿轮空档变速比不同。
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