CN1041551C - 连续可变速比的传动装置的改进 - Google Patents

连续可变速比的传动装置的改进 Download PDF

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CN1041551C
CN1041551C CN94190960A CN94190960A CN1041551C CN 1041551 C CN1041551 C CN 1041551C CN 94190960 A CN94190960 A CN 94190960A CN 94190960 A CN94190960 A CN 94190960A CN 1041551 C CN1041551 C CN 1041551C
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speed ratio
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CN1116875A (zh
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T·G·费洛斯
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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
    • 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
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
    • F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
    • F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
    • F16H2015/383—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces with two or more sets of toroid gearings arranged in parallel
    • 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
    • F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
    • F16H2037/0873—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft with switching, e.g. to change ranges
    • 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
    • F16H37/10—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 at both ends of intermediate shafts
    • F16H2037/104—Power split variators with one end of the CVT connected or connectable to two or more differentials

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Friction Gearing (AREA)
  • Structure Of Transmissions (AREA)
  • Hybrid Electric Vehicles (AREA)

Abstract

一种连续可变速比的传动装置(CVT)，其能换空档并能在至少两个档次下运行，且其包括一变换器(4)，一动力再循环行星装置(E)，一末端驱动轴(1)，它可通过两个轴(A，B)中的一个与变换器相连，和一输入行星装置(e)，其输入元件可与原动机(3)相连，其两个输出元件分别与轴(A，B)相连。动力再循环行星(E)与离合器(44，46)相连，从而动力在该档次下始终再循环。其他档次下则没有任何动力再循环。

Description

连续可变速比的传动装置的改进
本发明涉及一种连续可变速比的传动装置(CVT’S)。本发明广泛适用于这样一种连续可变速比的传动装置(CVT’S)。其中变换器，即速比变换部件不能达到零速比。也就是说，尽管输出元件的转速可在预定的范围内无级变换，同时输入元件以恒速转动，而输出速度范围不包含零输出速度。为使传动装置输送零输出速度，通常是由一行星齿轮装置的一个部件驱动连续可变速比的传动装置(CVT)的输出，它的另外两个部件通过需要的与行星装置速比相匹配的齿轮装置，而连接至变换器的输出和输入侧。当这种变换器和行星装置这样组合后，可能出现这样的情况：如果变换器输入速度保持恒定，然后变换器由其速比范围的一端移动至另一端，以使连续可变速比的传动装置(CVT)的输出速度连续变化，开始是由一个方向从最大速度下降至零输出速度，然而在某些情况下它可以由另一个方向升至最大速度。整个这一过程，(尤其是该领域称为“换空档”的那一时刻)，当输出速度为零速度时，行星装置将通过变换器和连续可变速比的传动装置(CVT)的其它部件再用循环动力。因而这类行星装置在该领域称为“再循环行星装置”。另外，也属于众所周知的是，连续可变速比的传动装置(CVT)包括一个带有连接于原动机上的一组件的第二或“输入”行星装置。
这也是该领域公知的，特别是当变换器属于环形轨道滚动牵引型时，通过引入齿轮装置和离合器来扩大连续可变速比的传动装置(CVT)的速比范围，从而变换器得以在多于一种“档次”下工作。也就是说，通过操纵离合器进行不同的换档时一旦该型式的变换器的滚子从其速比角度范围的一端摆至另一端，以将连续可变速比的传动装置(CVT)的输出速度从一个值转换到另一值，并且或许还伴随上述方向的变换，有可能使滚子沿反方向回摆过其运动范围，并以这种方式进一步转换连续可变速比的传动装置(CVT)的输出速度。这样，通过正确选择齿轮速比，有可能从一个档次转换到另一个档次，又不会瞬时改变任何速度。这种档次变化在该领域称为同步变换。
目前，一个包括如前所述已知特点的连续可变速比的传动装置的例子公开在英国专利说明书GB-A-1454702中，其中该连接可变速比的传动装置包括设置有两个单独的被驱动元件，而连续可变速比的传动装置的末端驱动轴交替地与上述被驱动元件相连。本发明的目的是提供一种环形轨道滚动牵引型的连续可变速比的传动装置。一个具有本发明特点的连续可变速比的传动装置的不同点在于，该传动装置使动力在仅包含空档的一档次下的再循环行星装置中被再循环，并且在其他档次下，连续可变速比的传动装置的输出端简单地与两个轴的一个轴相连，这两个轴即位于变换器的两侧又位于输入行星装置的两侧。这就避免了动力损失，而这种损失如果在某些或所有其他档次下也产生动力再循环则是不可避免的，并这也提供了实质性的潜在优点，这些优点包括减少特别是挖掘机等车辆的变换器尺寸，而这些车辆常常需要在低或零路面速度运行时输送大扭矩。
本发明的目的是提供一种环形轨道滚动牵引型的连续可变速比传动装置，它能换空档并能在至少两个档次下操作，具有特别方便的沿向前和退后两个方向附加档次的装置，并具有特别在换空档或邻近换空档状态下限制通过变换器动力的装置。这种动力限制呈现出提供有潜在的显著优点，包括减小变换器尺寸，特别是车辆例如挖掘机、卡车中的变换器的尺寸，这种卡车以低或零路面速度运动时，经常要求输出高扭矩。
本发明提供一种连续可变速比的传动装置(“CVT”)，它能换空档和能在至少两个档次下运行，且其包括一速比变换部件(“变换器”)，一再循环行星装置(E)，一输入行星装置(e)，输入行星装置的输入元件可通过轴2与一原动机相连，和一输出轴，它可与两个交替的被驱动的元件(A，B)中的一个相连，其特征在于，该再循环行星装置(E)与适当的离合器相连，从而在一个包括换空档的各档次的一个档次下动力通过该行星装置再循环，而在其余的一个或更多的档次下，没有任何动力在其中循环，动力通过另外的离合器传至该连续可变速比的传动装置(CVT)的输出轴，并且换成该档时两被驱动元件(A，B)中无论那一个的速度都会升高，而两被驱动元件(A，B)分别既与该变换器的两侧相连，又与该输入行星装置(e)的不同输出元件相连。
本发明由各权利要求来限定，并包括各简化示意附图所示的各连续可变速比的传动装置(CVT)。现结合这些附图，以举例方式对本发明进行说明，其中：
图1是一系统简图；
图2用图表形式来比较轴速度；
图3示出一种连续可变速比的传动装置(CVT)的实施例，和
图4示出图1所示系统简图的一种替换形式。
在图1中，一个具有一输出轴1和一输入轴2(用于与以标号3表示的原动机相连接)的连续可变速比的传动装置(CVT)包括一环形轨道变换器4，一再循环行星装置E(以标号5表示)和一输入行星装置e(以标号6表示)。标号7，8表示连接至变换器4的第一和第二运行元件上的轴。这些运行元件不能如通常那样简单地称为“输入”和“输出”元件，因为从下文将可看到，当连续可变速比的传动装置(CVT)在两个档次之间运动时它们会改变其功能。轴7，8通过轴A和B分别与输入行星装置e的两个组件(例如，太阳轮和行星轮架)相连接，行星装置e的第三个组件(例如齿圈)可与原动机3相连接。轴A和B还通过适当的传动装置与再循环行星装置E的两个组件(例如又与太阳轮和行星轮架)相连接，而该再循环行星装置E的第三组件(例如齿圈)，在包括转换空档的工况时，可借助低档离合器9与输出轴1相连接。因此，在图1所示的示意图中可以明显看出，轴A和B的转速(其转速直接与轴7和8的转速相关)，无论变换器4中的滚子怎样在它们角运动范围内改变走向，总是反相位运动的。这样，当滚子从该角运动范围的一端移动至另一端时，轴A和B中的一个将加速，而另一个就减速。然后当滚子如在下一个“档次”从另一端又移回来时，轴A和B的速度变化正好相反。
低速档时，离合器9将啮合，动力将通过行星装置E再循环，并且随着变换器4以其速比范围的一端进给至另一端，输出轴1的速度可设置成产生典型的连续的“低档”渐进，在一个方向上的从一个有限值下降至零，然后上升至在另一方向上的一第二个有限值。对所有其它所需档次来说，离合器9是脱开的，行星装置E停止再循环动力，而输出轴1借助一种齿轮传动／离合器组合(10，11；12，13；14，15；16，17；18，19；20，21等)的方式被无论轴A和轴B那个来驱动，以相应档次的最低速度起动，并升至该档次的最高速度。这样，随着换低速档(这时输出轴1向前转动)结束，并假设轴A然后以其最低速转动，离合器9会脱开啮合，而离合器11啮合，以将连续可变速比的传动装置(CVT)换成“中”前进档，这时输出轴1通过齿轮装置10被轴A驱动，直至轴A与B的相对速度达到反方向的极值为止，这时离合器11可能脱开啮合，而离合器13啮合，以进入另一“高”前进档，在此档中轴1通过另一组固定齿轮装置12由轴B驱动。但是，如果连续可变速比的传动装置(CVT)在到达低速档结束，此时输出轴1是沿反方向转动的，并且希望提供另一些“中”和“高”退后档次，并使连续可变速比的传动装置(CVT)通过这些档次进行，由于轴B仍以其最慢速转动，一典型的离合器操作顺序将是脱开9／啮合17，以通过固定齿轮装置16以“中退后速度”由轴B驱动输出轴；然后脱开17／啮合15，以通过固定齿轮装置14“高退后速度”由轴A驱动输出轴。标号18-21表示各离合器／齿轮装置组合，通过这些组合还可方便地增加另一些档次，前进档和退后档。变换器4，行星装置E和齿轮装置组10，12，14等的速度比当然可以该领域公知的方式进行选择，这样，两档次之间的离合器啮合／脱开啮合是同步实现的，如上所述，不会瞬时改变传动速比。
图2是输出轴1(X轴)的转速与轴A和B(Y轴)的转速之间的典型关系的简化示意图象。点25-28表示档次变化点，即分别代表低中前进，低中退后，中高前进和中高退后。应特别指出的是，X轴的比例尺是非线性的。如简化图所示，假定它是线性的，则各线在靠近Y轴时一般可能会变的特别陡，而随着各线沿两个方向远离Y轴，它们又可能会逐渐变得平缓。
图3示出本发明的实施例，其中与图1中已介绍过的那些零件直接相类似的零件，标以相同的标号。输入轴2驱动输入行星装置e的齿圈35，而太阳轮36驱动携带环形轨道变换器4的输入盘37的轴A(等于轴7)。标号38表示该变换器的两个可变走向的滚子(典型地总数为6个)，箭头39表示任一换档过程中各滚子发生倾斜以改变“速比角”从而改变传动比的方向。行星装置e的行星轮架40借助一齿轮链34与轴B相连，轴B(等于轴8)还与变换器4的输出盘41相连，而不被链42改变方向。轴A还携带着离合器44和45的一半，而轴B则携带着离合器46和47的一半。离合器47的另一半由连续可变速比的传动装置(CVT)的输出轴1携带。还设置了另外两个离合器48，49。
为接合到低档，应使离合器44，46啮合，而让所有其它离合器脱开啮合。借助离合器44，轴A驱动再循环行星装置E的太阳轮50。借助离合器46和一减速齿轮传动链51，轴B驱动行星轮架52。动力在行星装置E内再循环，并借助齿圈53和一减速齿轮传动链54将输出功率输送至轴1。当离合器44，46一起啮合时表现出图1中离合器9的作用。
为从低档转换到中前进档，应脱开离合器46，闭合离合器48。这具有“锁定”装置E的作用，这样该装置E再也不能再循环动力，而是作为一整体转动，动力通过太阳轮50，锁定的装置E和同一减速齿轮传动链54以轴A传递至输出轴1。离合器48这时相当图1中的离合器11。为从低档转换成中退后档，离合器49应啮合，离合器44应脱开啮合，同时离合器46保持啮合。这时动力从轴B通过离合器46，减速齿轮装置51，行星轮架52，离合器49和一减速齿轮传动链55传送至输出轴1，该减速齿轮传动链55还使运动相对于齿轮传动链54反向。这样，离合器49可相当图1中的离合器17，并且在这一换档过程中行星装置E的太阳轮50和齿圈53不传送任何动力。为在中高前进档之间进行换档，离合器44，48应脱开啮合，而离合器47啮合。动力这时通过啮合的离合器47直接从轴B传至轴1。为在中高倒车档之间进行换档，离合器46和49应脱开啮合，而离合器45应闭合，然后动力将从轴A通过啮合的离合器45和齿轮链55直接传送至输出轴1。这时离合器47和45相当于图1中的离合器13和15。
假定效率为100％，在任何连续可变速比的传动装置(CVT)的运行中，输入功率Pi(它等于输入轴2上产生的速度Ni和转矩Ti)必然等于输出功率Po(它等于输出轴1上产生的输出速度No和转矩To)。如结合图1和图3叙述过的本发明实施例中，通过变换器4传递的动力，除低速档之外的所有档次均可方便地设置成明显地小于Pi。然而在低速档，或许有时表明难以选择齿轮速比和其它相关参数，以防止最大变换器功率不适当地升高。环形轨道变换器需传递的最大功率在确定这类变换器的尺寸和成本时是一关键因素，因而存在减小该最大功率方面的明显优点。图4示出一种图1所示系统图的替换方案，其中输入轴2，输入行星装置e，变换器4和轴A和B之间的关系与前述相同，但再循环行星装置E改为与轴B，低速档离合器9和输入轴2相连，而不是如前那样与离合器9和轴A和B相连。箭头表示低速档时输入功率Pi和轴B的功率Pb的再循环，符号d表示一大于零但小于Pb的功率量。图4所示的实施例中还采用了另外的齿轮装置60，61和离合器62，63，以提供中档和更高的档次。离合器9，62和63均使驱动装置与侧轴64啮合，该侧轴在所有档次均沿同一转动方向被驱动。如果需要许多档次，采用图1那样的方案，会使齿轮和离合器的数量增加许多。而在图4所示的对称型“前进和退后”系统中，通过在下游提供前进和退后齿轮组65和66，齿轮和离合器的数量可减半。这样，低速档仅需满足输出速度从零转速附近(即换成空档)向下／中档沿一个方向同步变速即可。这种不对称方案使再循环行星装置E能与原动机(通过轴2)相连和仅与变换器4的一侧相连(通过轴B)，从而减少了通过变换器传递的功率。另一个应当指出的关于图4所示实施例的潜在优点是，在前进和退后驱动中均可采用较高档次的传动链。
由上述说明可以看出，本发明包括一连续可变速比的传动装置(CVT)，其中变换器不仅与一再循环行星装置相组合，而且至少该变换器的两侧中的一侧还与一第二个输入行星装置的一个部件相连，该第二个输入行星装置的另一部件可与原动机相连。然后再提供若干离合器和齿轮装置，动力便可在包括换成空档在内的档次中通过再循环行星装置再循环，再在后续的其它档次中再循环行星装置可被旁通，而动力可通过适当的离合器和齿轮装置传送到连续可变速比的传动装置(CVT)的输出端，当换成该档次时，从该变换器的任一侧输出的速度将升高。

Claims (4)

1．一种连续可变速比的传动装置(“CVT”)，它能换空档和能在至少两个档次下运行，且其包括一速比变换部件(“变换器”)(4)，一再循环行星装置(E)，一输入行星装置(e)，输入行星装置的输入元件(35)可通过轴2与一原动机(3)相连，和一输出轴(1)，它可与两个交替的被驱动的元件(A，B)中的一个相连，其特征在于，该再循环行星装置(E)与适当的离合器(44，46)相连，从而在一个包括换空档的各档次的一个档次下动力通过该行星装置再循环，而在其余的一个或更多的档次下，没有任何动力在其中循环，动力通过另外的离合器(48，47；49，45)传至该连续可变速比的传动装置(CVT)的输出轴(1)，并且换成该档时两被驱动元件(A，B)中无论那一个的速度都会升高，而两被驱动元件(A，B)分别既与该变换器(4)的两侧相连，又与该输入行星装置(e)的不同输出元件(36，40)相连。
2．如权利要求1所述的连续可变速比的传动装置(CVT)，其特征在于，具有至少3个档次，在至少其中一个档次下，输出轴(1)始终是沿前进方向转动的。
3．如权利要求2所述的连续可变速比的传动装置(CVT)，其特征在于在至少其中另一个档次下，输出轴始终是沿反方向转动的。
4．如上述权利要求之一所述的连续可变速比的传动装置，其特征在于所述变换器属于环形轨道滚动牵引型。
CN94190960A 1993-01-18 1994-01-12 连续可变速比的传动装置的改进 Expired - Fee Related CN1041551C (zh)

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CN102128244B (zh) * 2010-01-14 2015-05-06 福特全球技术公司 无级变速器
CN104822972A (zh) * 2012-08-10 2015-08-05 托罗特拉克(开发)有限公司 用于车辆的无级变速传动装置
CN104822972B (zh) * 2012-08-10 2019-02-12 艾里逊变速箱公司 用于车辆的无级变速传动装置

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GB2274315B (en) 1995-11-08
JPH08505460A (ja) 1996-06-11
GB9300862D0 (en) 1993-03-10
GB2274315A (en) 1994-07-20
DE69402410D1 (de) 1997-05-07
DE69402410T2 (de) 1997-07-31
GB9400473D0 (en) 1994-03-09
KR950704633A (ko) 1995-11-20
KR100314449B1 (ko) 2001-12-28
US5564998A (en) 1996-10-15
CN1116875A (zh) 1996-02-14
EP0679235B1 (en) 1997-04-02
JP3442779B2 (ja) 2003-09-02
IN189057B (zh) 2002-12-14
EP0679235A1 (en) 1995-11-02
WO1994016244A1 (en) 1994-07-21

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