CN107524718A - 具有与摆动角相关的摩擦装置的扭转减振器 - Google Patents
具有与摆动角相关的摩擦装置的扭转减振器 Download PDFInfo
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Abstract
本发明涉及一种扭转减振器,其具有至少一个扭矩输入盘和至少一个扭矩输出盘,其中,扭矩输入盘能够沿周向相对于扭矩输出盘克服至少一个弹簧储能器的力运动,相对运动由摩擦装置进行缓冲,摩擦装置在第一摆动角区域内比在第二摆动角区域内产生更小的摩擦力矩,为此摩擦装置具有至少两个能彼此相对地扭转的摩擦面,摩擦面通过至少一个摩擦环与扭矩输入盘的携动连接与摆动角相关地被激活,其特征在于,携动连接具有弹簧元件,该弹簧元件在功能上与摩擦装置串联地设置并且在功能上与弹簧储能器并联地设置。
Description
技术领域
本发明涉及一种具有与摆动角相关的摩擦装置的扭转减振器。
背景技术
通常的摩擦装置并非少见提前故障的问题。大部分的摩擦装置在整个扭转减振器特征曲线上以恒定的摩擦力矩/恒定的阻尼工作或者与一个特征曲线区域或一个弹簧级相协调。为此,例如在DE102007006381A1中,控制接片接合到弹簧窗中或者至少具有用于弹簧的控制边棱。然而,所需的摩擦力矩的大小仅由在变速箱的各个档位中传动系共振所需的阻尼确定。共振越大,则所需的阻尼(=摩擦力矩)越大,进而摩擦装置的负荷也越大。就通常的意义而言,负荷是在摩擦装置的接触位置处较大的力(多为盘簧),由此是较大的表面压力。
在例如在DE 102007006381 A1中的具有分级的摩擦力矩特征曲线的摩擦装置中,在两个摩擦力矩水平之间的过渡处出现强烈跳跃的转矩升高,其可视为在摩擦装置上的磨损。
一种解决方案可以是,摩擦装置的所述盘簧的预紧力设计成在摆动角上是可变的。例如参见DE 33 33 536 A1。然而,这种结构原理自身承受不小的磨损并且具有内摩擦力矩,其在设计整个摩擦装置时必须加以考虑。
发明内容
本发明的目的在于,使跳跃的转矩变化的不利作用最小化。
为了实现此目的,携动连接具有弹簧元件,该弹簧元件在功能上与摩擦装置串联地布置并且在功能上与弹簧储能器并联地布置。
与所说明的现有技术不同地,并未通过复杂的摩擦装置来解决问题,而是通过将摩擦装置的摩擦功与弹簧功组合的构思来解决。由此可以明显简单地构造摩擦装置。摩擦装置对扭转装置的弹簧储能器起缓冲作用,但连接在该弹簧储能器之前的弹簧元件不这样。因此,缓冲作用进一步精确地限制在摆动角区域上,如所期望的。
原则上,连接在摩擦装置之前的弹簧元件可以实施为拉力弹簧。然而,可能有问题的是弹簧元件的疲劳强度。为了实现特别稳定的解决方案,由接合到摩擦环的凹部中的携动销构成携动连接,其中,在携动销与凹部之间设置有弹簧元件。携动销与凹部的组合使弹簧元件压成块。然而,也可行的是,栓并未实施为圆形,而是实施为边条,使得栓在摆动角的结束处以减小的摩擦贴靠在凹部处并且弹簧元件的弹簧行程并未完全用尽,这又有利地影响弹簧元件的使用寿命。
也可以规定,沿摆动角方向在携动销的两侧设置有至少一个弹簧元件。这种结构方式的优点在于,两个并联连接的弹簧在选择弹簧元件和设定弹簧元件的尺寸时提供很大的灵活性。
一种特别节省空间的方案的特征在于,弹簧元件实施为片簧。此外,片簧可以利用少量的物料体积产生相对较大的弹力并且在离心作用下其弹簧特性不那么显著地变化。
也可以规定,弹簧元件实施为螺旋压力弹簧。
在使用两个弹簧元件的情况下,这两个弹簧元件可以具有不同的预紧。由此能够针对性地匹配进出摩擦装置的作用区域的过渡。
弹簧元件也可以构造为弹性体材料体。弹性体材料体除弹簧作用之外还具有自阻尼。由此,通过存在阻尼而增大了扭转减振器的摆动角区域。
在一种实施方式中,携动销例如在涂层的范围内承载弹簧元件。由此省去了固定弹簧元件的必要性。代替地也可以将弹簧元件容纳在凹部中。此外,简单地制造被压在凹部中的环形元件。
附图说明
根据以下部件详细说明本发明。
附图中:
图1示出了具有摩擦片的扭转减振器,
图2至图5示出了扭转减振器的剖视图,
图6示出了图1的放大图,
图7至图8示出了图6的替代变型,
图9示出了图7和图8的代替图,
图10示出了具有弹簧元件的摩擦装置的特征曲线。
具体实施方式
图1示出了具有扭转减振器3的部分组装的离合器盘1的前视图。原则上,扭转减振器也可应用在离合器盘之外。结合图2和图3明显可见,扭转减振器3具有扭矩输入盘5,其承载摩擦片7。在该扭矩输入盘5上,例如驱动马达的扭矩通过未示出的离合器壳体传递到摩擦片上。
扭矩输入盘5具有窗式的缺口9,在其中设置有至少一个弹簧储能器11、例如螺旋压力弹簧。在此示例中,在螺旋压力弹簧的端匝与缺口9之间插入支撑盘13。
扭矩输入盘5在其内径上相对于扭转减振器毂15对中。示例性地,扭转减振器毂15实施为分切的,在其中外环17可以沿周向实施限定的位移行程。通过齿廓19形成与内毂的连接。在外环17与内毂21之间的相对运动通过所谓的预阻尼器缓冲。预阻尼器23的作用方式和结构例如由DE 199 58 326 A1已知。预阻尼器23和分切的扭转减振器毂是可选的。
此外,扭转减振器3包括两个扭矩输出盘25、27,其设置在扭矩输入盘5的两侧。扭矩输出盘25、27也具有窗式的缺口29,弹簧储能器11接合到该缺口中。根据在扭矩输入盘5和扭矩输出盘25、27中的弹簧储能器11和窗式的缺口9、29的尺寸,两个盘组可以沿周向相对于彼此运动。例如通过铆接连接部31,两个扭矩输出盘25、27沿轴向且沿周向与外环17刚性连接。在外环17的两侧可以可选地设置有防磨损盘33、35,其由铆接连接部31保持,使得防磨损盘33、35沿周向相对于扭矩输出盘25、27位置固定被支承。在此,防磨损盘33、35以其摩擦面37、39指向扭矩输入盘5的方向(见图4和图5)。
在扭矩输入盘5与扭矩输出盘之间的相对运动由摩擦装置41缓冲。摩擦装置包括具有摩擦面的第一组摩擦环43、45、47、61,其沿周向相对于扭矩输出盘25、27位置固定被支承并且直接在扭矩输入盘5的两侧贴靠在该扭矩输入盘上。所述摩擦环43-47例如可以由金属材料制成,以便一方面可以利用高的耐磨性并且另一方面可以利用相对高的摩擦系数。第一组的摩擦环43、45、47在其外直径区域处具有用于间隔栓51的凹部49,该间隔栓横向地延伸穿过扭转减振器3并且穿过扭矩输出盘25、27的外侧的覆盖面53、55,必要时与覆盖面53、55填密。摩擦环43-47中的凹部49的尺寸沿周向设定成,为装配提供一定的间隙,否则没有额外的自由进入空间。
扭矩输入盘5具有用于间隔栓51的贯穿横截面57,其中,贯穿横截面57沿周向至少设定成与扭转减振器3的设置的整个摆动角一样大。
扭转减振器具有带有摩擦面的第二组摩擦环59、61,其在扭转减振器3的第一摆动角区域中相对于扭矩输入盘5和相对于扭矩输出盘25、27被支承。第二组的摩擦环59、61分别设置在第一组的摩擦环43-47与扭矩输出盘25、27之间。只要存在防磨损盘33、35,第二组的摩擦环就位于防磨损盘33、35与第一组的摩擦环43-47之间。原则上,两个摩擦环组中的摩擦环43-47、59、61也可以具有不同的摩擦系数,使得例如第一组的摩擦环43-47具有较小的摩擦系数并且为此例如由塑料制成。
第二组摩擦环59、61通过扭矩输入盘5的多个携动销63、65控制。所述携动销可以直接从扭矩输入盘的材料中成形。然而,在此示例中,携动销63、65由单独的栓67构成,其牢固地锚固在扭矩输入盘中。摩擦环59、61的操控通过在携动销63、65或者说栓67与摩擦环59、61中的凹部69之间的携动连接实现,所述栓接合到所述凹部中。凹部69的尺寸沿周向设定成当已经历过扭转减振器3的第一摆动角范围71时携动连接才闭合。为了使碰撞噪声及摩擦环59、61的磨损最小化或避免碰撞噪声及摩擦环59、61的磨损,在携动销63、65或者说栓67之间设置有弹簧元件73(见图4及图6)。具体地,栓67在此实施例中承载弹性体材料体,其优选由涂层构成。然而,也存在如下可行方案:弹簧元件73被容纳在摩擦环59、61的凹部69中,如图6所示。其中可看到与第一摆动角区域71的携动连接和在间隔栓51与第一组的摩擦环59之间的沿周向不可相对旋转的连接。此外,在第二组的摩擦环59中可看到自由进入空间75,其沿周向描述了整个摆动角。
优选结构形式为盘簧的弹簧组件77对整个摩擦装置41施加轴向的预紧力。在此,两个扭矩输出盘25、27构成轴向支撑元件。图2至图5示出了摩擦装置41也可以具有奇数个摩擦环。如此,例如在盘簧77与扭矩输入盘5之间直接并排地设置有第一组的两个摩擦环45、47,以便达到确定的轴向长度。通过这种措施可以确定轴向的安装空间79并由此确定盘簧77的预紧。
在图7中弹簧元件73实施为片簧并且设置在栓67的两侧。通过弹簧元件73的基本上径向的布置,其仅在很小程度上与离心力相关。
通过图8示出了原则上也可使用螺旋压力弹簧作为弹簧元件73。
图9示出了在栓67、弹簧元件73与凹部69之间的携动连接的代替模型。弹簧元件73设置在栓67的两侧。原则上,至少三种基本的弹簧协调是可行的。两个弹簧元件73在第一摆动角区域71的结束处具有剩余预紧。代替地,弹簧元件也可以在第一摆动角区域71的结束处失去预紧或者至少一个弹簧元件73已经在基础位置上(如在图9中所示)实际上没有任何值得一提的预紧。在这些基础设定之间可以存在任意的中间形式和组合,从而从弹簧元件73的弹簧功至摩擦装置41的摩擦功的过渡能够设计得非常多样化,如图10所示。摩擦装置41的特征曲线包括在摆动角区域71、81的两个摩擦力矩区域83、85之间的摩擦力矩的近似直角的过渡。弹簧元件的弹簧功的区域87位于前方,其可以通过弹簧元件73的特性例如线性地或逐渐增大地确定。
在通过扭矩输入盘5引入扭矩时,其沿周向相对于扭矩输出盘25、27转动。弹簧储能器11在此产生在整个摆动角上增加的反作用力矩。在第一摆动角区域71中存在第二组的摩擦环59、61与扭矩输入盘5之间的相对运动。由此,也产生由摩擦装置45引起的摩擦力矩。栓67可以在第一摆动角区域中沿周向运动,而第二组的摩擦环59、61不实施扭转运动。由此,第二组的摩擦环59、61与扭矩输出盘25、27共同作用地不产生摩擦力矩并由此也不承受磨损。
当第一组的摩擦环43-47的摩擦系数小于第二组的摩擦环时,也仅很小的摩擦力矩起作用。当在第一摆动角区域71的结束处在栓67与第二组摩擦环59、61之间的携动连接闭合并且一个或多个弹簧元件73在携动连接中被最大地预紧时,第二摆动角区域81开始并且除了第一组43-47与扭矩输入盘5的相对运动之外发生与扭矩输入盘5同步的在第二组的摩擦环59、61与防磨损盘33、35和第一组的摩擦环43-47之间的相对运动。附加地,摩擦环43与59以及47与61摩擦。第二组的摩擦环59、61具有较大的摩擦系数,并且通过附加的两个摩擦面副,摩擦力矩在第二摆动角区域中明显增大。因此,弹簧元件73在功能上与摩擦装置串联地连接并且在功能上与弹簧储能器并联地连接。
附图标记:
1 离合器盘
3 扭转减振器
5 扭矩输入盘
7 摩擦片
9 缺口
11 弹簧储能器
13 支撑盘
15 扭转减振器毂
17 外环
19 齿廓
21 内毂
23 预阻尼器
25 扭矩输出盘
27 扭矩输出盘
29 缺口
31 铆接连接部
33 防磨损盘
35 防磨损盘
37 防磨损盘的摩擦面
39 防磨损盘的摩擦面
41 摩擦装置
43 第一组的摩擦环
45 第一组的摩擦环
47 第一组的摩擦环
49 凹部
51 间隔栓
53 覆盖面
55 覆盖面
57 贯穿横截面
59 第二组的摩擦环
61 第二组的摩擦环
63 携动销
65 携动销
67 栓
69 凹部
71 第一摆动角区域
73 弹簧元件
75 自由进入空间
77 弹簧组件
79 轴向的安装空间
81 第二摆动角区域
83 摩擦力矩区域
85 摩擦力矩区域
Claims (8)
1.扭转减振器(3),其具有至少一个扭矩输入盘(5)和至少一个扭矩输出盘(25、27),其中,所述扭矩输入盘(5)能够沿周向相对于所述扭矩输出盘(25、27)克服至少一个弹簧储能器(11)的力运动,相对运动(41)由摩擦装置进行缓冲,所述摩擦装置在第一摆动角区域(71)内比在第二摆动角区域(81)内产生更小的摩擦力矩,为此所述摩擦装置(41)具有至少两个能彼此相对地扭转的摩擦面(43-47、59、61),所述摩擦面通过至少一个摩擦环与扭矩输入盘的携动连接与摆动角相关地被激活,其特征在于,所述携动连接(63-69)具有弹簧元件(73),该弹簧元件在功能上与所述摩擦装置(41)串联地设置并且在功能上与所述弹簧储能器(11)并联地设置。
2.按照权利要求1所述的扭转减振器,其特征在于,所述携动连接(63-69)由接合到所述摩擦环(59、61)的凹部(69)中的携动销(63、65)形成,其中,在所述携动销(63、65)与所述凹部(69)之间设置有弹簧元件(73)。
3.按照权利要求1所述的扭转减振器,其特征在于,沿摆动角方向在所述携动销(63、65)的两侧设置有至少一个弹簧元件(73)。
4.按照权利要求1所述的扭转减振器,其特征在于,所述弹簧元件(73)为片簧。
5.按照权利要求1所述的扭转减振器,其特征在于,所述弹簧元件(73)为螺旋压力弹簧。
6.按照权利要求3所述的扭转减振器,其特征在于,两个弹簧元件(73)具有不同的预紧。
7.按照权利要求1所述的扭转减振器,其特征在于,所述弹簧元件(73)由弹性体材料体形成。
8.按照权利要求2所述的扭转减振器,其特征在于,所述弹簧元件(73)容纳在所述凹部(69)中。
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CN113056625A (zh) * | 2018-11-15 | 2021-06-29 | 采埃孚股份公司 | 扭振减振组件 |
CN114060660A (zh) * | 2021-11-15 | 2022-02-18 | 广州婉迪科技有限公司 | 基于物联网的远程监控设备 |
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CN110388409A (zh) * | 2018-04-19 | 2019-10-29 | 南京法雷奥离合器有限公司 | 扭转减振阻尼器 |
CN110439968B (zh) * | 2018-05-04 | 2023-04-07 | 南京法雷奥离合器有限公司 | 扭转减振阻尼系统 |
DE102019204365A1 (de) * | 2019-03-28 | 2020-10-01 | Zf Friedrichshafen Ag | Kupplungsscheibe |
US11174903B1 (en) * | 2019-05-28 | 2021-11-16 | Logan Clutch Corporation | Clutch assembly and system |
JP7380540B2 (ja) * | 2020-12-18 | 2023-11-15 | トヨタ自動車株式会社 | 捩り振動低減装置 |
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US20170363151A1 (en) | 2017-12-21 |
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