CN115217944A - 具有轴向间隙补偿的传动机构-驱动单元 - Google Patents
具有轴向间隙补偿的传动机构-驱动单元 Download PDFInfo
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Abstract
本发明涉及一种尤其用于对机动车中的活动的部件进行调节的传动机构‑驱动单元(10),该传动机构‑驱动单元具有传动机构壳体(15)和沿着纵向方向(30)在传动机构壳体中得到支承的轴(18),所述轴通过轴向的止挡面(35)支撑在传动机构壳体(15)处的配对止挡面(36)上,其中为了对所述轴(18)进行轴向间隙补偿,楔形的构件(44)以借助于弹簧元件能横向于纵向方向(30)移动的方式来布置,并且所述楔形的构件(44)将止挡面(35)轴向地朝向所述配对止挡面(36)挤压,其中弹簧元件被构造为围圈弹簧(50,该围圈弹簧在第一径向侧(51)上固定地与楔形的构件(44)连接成预装配的单元(60)。
Description
技术领域
本发明涉及一种根据独立权利要求所述类型的、尤其用于对于机动车中的活动的部件进行调节的传动机构-驱动单元。
背景技术
利用DE 198 545 35 A1已知一种用于机动车刮水设备的驱动装置,所述驱动装置具有壳体和一根以能旋转的方式在其中得到支承的、带有螺杆的电枢轴。借助于轴向力产生装置,在此使楔形滑动件径向于电枢轴地移动,以用于对于电枢轴的轴向间隙进行补偿。所述楔形滑动件的移动力通过被预紧的弹簧元件来施加,该弹簧元件将楔形滑动件径向地朝向所述电枢轴的止挡挤压,由此该电枢轴被轴向移动直至对于轴向间隙进行补偿。在从动轮上存在强烈负荷时在所述电枢轴上出现轴向力,用该轴向力将所述电枢轴朝向楔形滑动件挤压,从而在此将该楔形滑动件径向地离开电枢轴地朝向所述弹簧元件返回地挤压。所述弹簧元件的这样强烈的持久负荷导致以下结果,即:所述弹簧元件的使用寿命或者其弹性特性减弱并且因此所述电枢轴的轴向间隙不再得到补偿。由此,所述电枢轴可能在负荷下轴向地来回运动,这可能导致不舒服的喀嚓声。
发明内容
本发明优点
具有独立权利要求的特征的、按本发明的传动机构-驱动单元具有以下优点,即:通过使用用于将楔块径向地压入的围圈弹簧(Schlingfeder),能够在整个使用寿命期间提供一种非常稳健的、具有高的弹簧刚性的轴向间隙补偿方案。随着所述传动机构壳体的盖的装配,所述围圈弹簧在径向上被预紧,并且由此能够在所述装置的整个使用寿命期间将楔形的构件径向地补充推移,以用于消除所出现的轴向间隙。相对刚性的围圈弹簧的所储存的能量导致以下结果,即:这样的自行调节的轴向间隙补偿在所述传动机构-驱动单元的整个使用寿命期间以足够的力将楔形的构件径向地朝向所述轴挤压。通过将所述围圈弹簧与楔形的构件集成为预装配的单元的这种集成方式,一方面能够通过构件的减少来简化所述装配,并且另一方面即使在强烈的负荷力矩起作用时也能够确保所述弹簧相对于楔形的构件的以及相对于传动机构壳体盖的更加可靠的精确的定位。
通过在从属权利要求中所说明的措施,能够实现根据独立权利要求所述的装置的有利的改进方案。所述围圈弹簧有利地被构造为扭转弹簧,该扭转弹簧径向地被压缩在楔形的构件与传动机构壳体、尤其是传动机构盖之间。在此,所述围圈弹簧横向于其扭转轴线地以第一径向侧径向地支撑在楔形的构件上,并且以对置的第二径向侧径向地支撑在传动机构壳体、尤其是其盖上。在此,所述预装配的单元能够与壳体盖一起沿着相对于轴的径向方向来安装。
所述楔形的构件与楔尖径向对置地具有较宽的楔背,所述围圈弹簧形状锁合地被固定在所述楔背上。在此有利的是,所述背部的整个宽度沿着轴向方向用于让围圈弹簧抵靠,由此能够实现在所述围圈弹簧与所述楔形的构件之间的非常可靠的固定的连接。
特别有利的是,在所述背部的区域中在所述楔形的构件的塑料中成形了槽,所述围圈弹簧的径向向外伸出的自由端部嵌合到所述槽中。在此,所述围圈弹簧的较硬的外部的自由端部与较软的槽构成压配合,使得所述围圈弹簧可靠地保持被固定在楔形的构件中。作为替代方案,所述围圈弹簧也能够借助于卡锁连接被固定在楔形的构件上。
所述槽的几何形状构成了在所述背部上横向于轴向方向的突起,使得所述被压入到槽中的自由端部关于所述预装配的单元的安装方向形成侧凹。通过所述槽的这种迷宫式的造型,所述围圈弹簧关于横向于纵向方向的整个平面形状锁合地与楔形的构件相连接。
为了也关于轴向方向将所述围圈弹簧牢固地固定在槽中,在所述外部的自由端部上优选成形了比如呈小的卡钩的形式的卡锁元件,所述卡锁元件锁定在槽壁中。在此,所述卡锁元件能够形成关于轴向方向的倒钩,或者也能够构成关于槽方向的额外的形状锁合。
所述弹簧刚性以及尤其是其最终位置渐进(Endlagenprogression)也能够通过搭接角来预先给定,所述径向内部的端部以所述搭接角与所述围圈弹簧的径向外部的圈进行搭接。这个搭接角在未经受负荷的状态中比如能够为20°到90°,或者在较高的刚性要求的情况下也能够为90°到270°。
在安装所述预装配的单元之后,所述径向内部的端部径向于扭转轴线地支撑在径向外部的圈上。在沿着径向方向的外部负荷变化时(由于所述楔形的构件的径向运动),在此所述内部的端部切向地沿着外部的圈移动,由此所述围圈弹簧的总直径发生变化。这样的扭转弹簧具有较小的弛豫特性(Relaxationsverhalten),并且由此在整个使用寿命期间提供用于楔形的构件的足够的径向的压紧力。
所述围圈弹簧的弹簧刚性也能够通过其横截面来预先给定。所述围圈弹簧有利地由具有矩形的横截面的板条来成形。而后使所述板条螺旋形地弯曲,使得所述矩形的横截面的较大的延伸部沿着纵向方向平行于围圈弹簧的扭转轴线来延伸。由此,所述围圈弹簧能够以沿着轴向方向较宽的抵靠面抵靠在楔形的构件上并且抵靠在壳体上,由此能够沿着所述预装配的单元的安装方向实现明确地限定了的力的传递。
为了这样明确地限定地将力传递到所述楔形的构件上,在这个构件上成形了部分圆形的***,所述围圈弹簧的第一径向侧在其横截面的整个轴向延伸度的范围内嵌合到所述***中。由此,所述围圈弹簧的圆形的外侧面在较大的角度范围内形状锁合地抵靠在所述楔形的构件的背部中的对应的成形部中。由此防止所述围圈弹簧相对于楔形的构件的安装方向发生倾斜。
所述按本发明的用于产生轴向力的预装配的单元不仅能够布置在所述轴的端侧上而且能够布置在所述轴的凸缘上,从而为所述传动机构-驱动单元的不同的实施方式保证了高的变化性。比如,在所述轴上布置了蜗轮,所述蜗轮的凸缘形成了用于轴向的启动盘的轴向的启动面。所述楔形的构件在轴向上直接抵靠在这个启动盘上,所述楔形的构件在与启动盘轴向对置的情况下在轴向上支撑在传动机构壳体上。在这种实施方式中,所述轴的另一个止挡面通过楔形的构件在轴向上被朝向壳体的对应的配对止挡面挤压。所述止挡面能够优选地被构造在所述轴的端侧上或者被构造在另一凸缘上比如蜗轮上。作为替代方案,所述楔形的构件连同所集成的围圈弹簧也能够布置在轴的端侧上,并且将所述轴的凸缘在轴向上朝向传动机构壳体挤压。
如果所述轴具有比如与蜗轮啮合的螺杆齿部,则在比如使活动的部件朝向止挡移动时出现很高的轴向的轴力(Wellenkraft)。同样,对于所述轴的具有主轴螺纹的主轴驱动装置来说,在活动的部件加速或者减速时可能出现强烈的轴向力。所述主轴比如能够通过电马达来驱动,所述电马达能够将输出力矩经由螺杆传递到主轴的径向外部的螺杆齿部上。在调节过程中出现的动态的轴向间隙通过所述按本发明的预装配的单元来可靠地并且长期地得到补偿。
如果所述楔形的构件具有U形的外形,那也能够将所述构件特别有利地用于贯穿的主轴。所述楔形的构件优选未布置在主轴的端侧上,而是包围主轴并且比如支撑在一个在所述主轴上所制作的凸缘上。所述凸缘优选在轴向上被构造在蜗轮上,所述蜗轮对于旋转主轴来说抗扭转地布置在主轴上或者对于贯穿的主轴来说可旋转地布置在主轴上。
为了安装所述传动机构-驱动单元,首先将所述轴与蜗轮装入到在径向上敞开的传动机构壳体中,使得所述轴抵靠在传动机构壳体的径向的支承座中。将与楔形的构件相连接的围圈弹簧的所述预装配的单元同样沿着径向方向装入到传动机构壳体的基体里的楔形的缝隙中。此后,径向地安装并且固定所述传动机构壳体的盖,由此产生了作用到所述围圈弹簧上的预应力,所述预应力将所述楔形的构件径向地挤压到楔形的缝隙中。通过所述楔块,在此尤其通过单独地构造的止挡板将所述轴轴向地朝向壳体的配对止挡进行挤压,由此可靠地消除所述轴的轴向间隙。在径向地安装所述盖时,所述围圈弹簧以与楔形的构件对置的第二径向端部嵌合到所述盖的内侧面上的圆形的成形部中。通过这种圆形的拱起在所述盖中导引所述围圈弹簧,从而将弹力精确地沿着安装方向传递到所述楔形的构件上。
附图说明
本发明的另外的优点、特征和细节从以下对于优选的实施例的描述中并且借助于附图来得出。其中:
图1示出了传动机构-驱动单元的第一种实施例;
图2示出了预装配的结构单元的另一种实施例;并且
图3示出了按照图3的另一种变型方案的详细视图。
具体实施方式
在图1中示出的实施例以剖面示出了一种按本发明的传动机构-驱动单元10,其中电马达12通过蜗轮蜗杆传动机构14来驱动作为主轴20来制作的轴18,该轴从蜗轮蜗杆传动机构14的传动机构壳体15中伸出。在所述轴18上抗扭转地布置了蜗轮24,该蜗轮具有轴向的凸缘22。这个凸缘22形成第一启动面25,该第一启动面支撑在启动盘28的配对启动面26上。楔形的构件44轴向地抵靠在所述启动盘28上,所述楔形的构件通过围圈弹簧50横向于纵向方向30被压入到在启动盘28与传动机构壳体15之间的楔形的缝隙40中。所述围圈弹簧50在第一径向侧51上固定地与楔形的构件44相连接,并且由此与楔形的构件44构成预装配的单元60。所述楔形的构件44将轴向力施加到轴18上,该轴向力将所述轴18通过轴向止挡35朝传动机构壳体15的配对止挡面36挤压,该配对止挡面比如被构造在单独的起动板上。通过所述围圈弹簧50的径向的弹力将所述楔形的构件44不断地如此程度地压入到楔形的缝隙40中,从而可靠地消除所述轴18的轴向间隙。因此,能够在整个使用寿命的范围内通过预装配的单元60对于传动机构构件的制造公差和磨损进行补偿。所述轴18被支承在传动机构壳体15的径向的支承座32上,并且由传动机构壳体盖16的径向的支承套(Lagerstutzen)33径向地朝支承座32挤压。在所述传动机构壳体盖16上成形了圆形的拱起54,所述围圈弹簧50的第二径向侧52径向地嵌合到所述圆形的拱起中。在此,在径向地安装所述传动机构壳体盖16时所述围圈弹簧50被预紧,使得该围圈弹簧引起朝向轴18的作用到楔形的构件44上的径向的弹力。在图1中,所述主轴20被构造为旋转主轴(Drehspindel),其中所述止挡面35在端侧被构造在主轴20的轴向端部21上。在所述主轴20的轴向延长部中在这里在所述传动机构壳体16上构造有接纳部11,借助于该接纳部使得所述传动机构-驱动单元10能够以能回转的方式尤其在车身件或座椅件处被固定。在所述主轴20的对置的端部19上,主轴螺母80以能旋转的方式布置在主轴20的主轴螺纹78上,其中尤其所述主轴螺母80与对应的座椅件或车身件相连接。对于这样的旋转主轴来说,所述楔形的构件44连同所集成的围圈弹簧50也能够轴向地布置在主轴20的端部21与传动机构壳体之间,使得所述楔形的构件44沿着主轴20的旋转轴线对于该主轴进行轴向支撑。
在一种作为替代方案的实施方式中,所述主轴20能够被构造为贯穿的主轴,其中比如所述止挡面能够被构造在蜗轮24的第二凸缘23上,所述第二凸缘通过配对止挡面36来支撑在传动机构壳体15上。在此,尤其通过可旋转地布置在主轴螺纹78上的主轴螺母利用外部的螺杆齿部沿着纵向方向30来调节所述贯穿的主轴。所述电马达12比如具有一根带有螺杆72的输出轴71,所述螺杆与主轴18的螺杆齿部74或者按照图1的蜗轮24啮合。
图2示出了预装配的单元60的另一种变型方案,该预装配的单元由具有集成的围圈弹簧50的楔形的构件44连同传动机构壳体盖16所组成。所述楔形的构件具有尖部45,该楔形的构件44以所述尖部径向地被导入到楔形的缝隙40中。在与所述尖部45径向对置的情况下,在所述楔形的构件44上构造有背部46,该背部具有比尖部45大的沿着纵向方向30的延伸度。在所述背部46上成形了部分圆形的***91,所述围圈弹簧50的第一径向侧51嵌合在所述***上。在所述第一径向侧51上成形了径向外部的自由端部55,该自由端部被***到在背部46上所成形的槽58中。所述外部的自由端部55沿着纵向方向形状锁合地被压入到所述槽58中。所述槽58的几何形状对于所述外部的径向的端部55构成关于径向方向31的侧凹。所述外部的自由端部55比如为U形或者被折弯了两次大约90°,使得所述外部的自由端部55横向于纵向方向30地包围着突起59。作为替代方案,所述外部的自由端部55与对应的槽58形成迷宫结构。所述楔形的构件44优选由塑料制成,所述围圈弹簧50由弹簧钢来成形,其中所述围圈弹簧50的扭转轴线差不多沿着纵向方向30来伸展。所述围圈弹簧50在这里包围大约400°的缠绕角,从而在围圈弹簧50的径向外部的圈48与径向内部的端部56之间形所搭接区域。所述径向内部的端部56在此径向地支撑在径向外部的圈48上。所述搭接区域在这种实施方式中为大约30°到50°。所述围圈弹簧50的第二径向侧52沿着径向方向31抵靠在传动机构壳体盖16的圆形的拱起54中。所述围圈弹簧50由具有矩形的横截面62的金属条来形成。在此,所述横截面62的沿着纵向方向30的尺寸64被构造得大于该横截面62的横向于纵向方向30的尺寸66。由此,所述围圈弹簧50在其第一径向侧51处面状地处于在背部46中的部分圆形的***91中,并且其第二径向侧52处面状地抵靠在传动机构壳体盖16中的圆形的拱起54上。由此防止所述围圈弹簧50从径向平面中倾斜出来。在与圆形的拱起54轴向相邻的情况下,模制了所述传动机构壳体盖16的至少一个径向的支承套33,所述支承套将轴18径向地朝传动机构壳体15的径向的支承座32挤压。所述楔形的构件44在这里U形地构造有两条平行的支腿42,所述支腿通过背部46来彼此连接。所述支腿42在安装状态中包围着轴18。在一种作为替代方案的实施方式中所述楔形的构件44相对于轴18布置在端侧,在该实施方式中所述楔形的构件44被构造为全面状的楔块。
在图3中示出了所述预装配的结构单元60的另一种实施方式。所述围圈弹簧50的径向外部的自由端部55在这里V形地弯曲并且包围着尖的突起59,所述槽58构成所述尖的突起,以用于构造在所述围圈弹簧50与楔形的构件44之间的形状锁合的固定的连接。在所述径向外部的端部55上,在这里成形有卡锁元件68、比如卡锁凸起,所述卡锁元件在压入到槽58中时切入到所述楔形的构件44的塑料中。尤其在这里,在所述槽58上构造了导入段(Einführphase)69,以用于使所述外部的自由端部55沿着纵向方向30朝槽58中的压入变得容易。所述第一径向侧51又抵靠在背部46中的***91上。所述围圈弹簧50的径向外部的圈48与径向内部的端部56的搭接区域在这里构造得较大并且为大约180°到300°,由此比如产生540°到660°的总缠绕角。在所述径向内部的端部56的最外面的端部上,所述围圈弹簧50的材料径向向里弯曲,以便在存在所述围圈弹簧50的径向负荷时所述径向内部的端部56能够沿着径向外部的圈48切向地运动,而没有钩卡。
要说明的是,关于在附图和说明书中所示出的实施例,各个特征彼此间的多种多样的组合可行方案是可能的。所述按本发明的传动机构-驱动单元优选用在贯穿的主轴驱动装置或者旋转主轴驱动装置中,但是也能够用于将具有任意的传动元件的轴支承在其他的传动机构结构形式中。按本发明的将围圈弹簧50集成到楔形的构件44中的原理也能够运用于贯穿的主轴,对所述贯穿的主轴来说所述蜗轮被构造为主轴螺母并且具有与主轴螺纹78啮合的内螺纹。在此,所述主轴抗扭转地得到支承并且线性地轴向地穿过蜗轮来运动。大体上所描述的主轴驱动装置能够以多种多样的方式和方法来改动或修改,而不偏离发明构思。因此,能够将所述楔形的构件44布置在(所述蜗轮24)的凸缘22上或者在端侧布置在所述轴18上。同样,所述楔形的构件44的及围圈弹簧50的以及对应的槽58的及部分圆形的***91的几何形状和横截面62能够与具体的应用相匹配。所述独创性的电的主轴驱动装置10尤其适合用于调节机动车中的活动的组件、尤其是用于调节转向柱或者座椅组件。
Claims (14)
1.尤其用于对于机动车中的活动的部件进行调节的传动机构-驱动单元(10),所述传动机构-驱动单元具有传动机构壳体(15)和沿着纵向方向(30)在所述传动机构壳体中得到支承的轴(18),所述轴通过轴向的止挡面(35)支撑在所述传动机构壳体(15)的配对止挡面(36)上,其中,为了对于所述轴(18)进行轴向间隙补偿,楔形的构件(44)以借助于弹簧元件能横向于纵向方向(30)移动的方式来布置,并且所述楔形的构件(44)将所述止挡面(35)轴向地朝向所述配对止挡面(36)挤压,其特征在于,所述弹簧元件被构造为围圈弹簧(50),所述围圈弹簧在第一径向侧(51)上固定地与所述楔形的构件(44)连接成预装配的单元(60)。
2.根据权利要求1所述的传动机构-驱动单元(10),其特征在于,所述围圈弹簧(50)以与所述第一径向侧(51)对置的第二径向侧(52)沿着径向方向(31)支撑在传动机构壳体(15)上、尤其是支撑在传动机构壳体盖(16)上。
3.根据权利要求1或2中任一项所述的传动机构-驱动单元(10),其特征在于,所述楔形的构件(44)以尖部(45)指向所述轴(18)并且以较宽的背部(46)在径向上离开所述轴(18)地指向,并且所述围圈弹簧(50)的第一径向侧(51)形状锁合地抵靠在所述楔形的构件(44)的背部(46)上。
4.根据前述权利要求中任一项所述的传动机构-驱动单元(10),其特征在于,在所述背部(46)上沿着轴向方向(30)成形了槽(58),所述围圈弹簧(50)的径向外部的自由端部(55)嵌合到所述槽中。
5.根据前述权利要求中任一项所述的传动机构-驱动单元(10),其特征在于,所述围圈弹簧(50)的径向外部的自由端部(55)向外弯曲,并且所述槽(58)形成了关于径向方向(31)的用于径向外部的自由端部(55)的侧凹。
6.根据前述权利要求中任一项所述的传动机构-驱动单元(10),其特征在于,所述楔形的构件(44)由塑料构造,并且所述围圈弹簧(50)的外部的自由端部(55)沿着纵向方向(30)被压入到所述槽(58)中,并且尤其在所述外部的自由端部(55)上成形了卡锁元件(68),所述卡锁元件在压入时锁定在所述槽(58)中。
7.根据前述权利要求中任一项所述的传动机构-驱动单元(10),其特征在于,所述围圈弹簧(50)具有至少360°的缠绕角并且尤其具有从360°到640°延伸的搭接范围。
8.根据前述权利要求中任一项所述的传动机构-驱动单元(10),其特征在于,所述围圈弹簧(50)具有径向内部的端部(56),所述径向内部的端部径向地支撑在所述围圈弹簧(50)的径向外部的圈(48)上。
9.根据前述权利要求中任一项所述的传动机构-驱动单元(10),其特征在于,所述围圈弹簧(50)由具有矩形的横截面(62)的弹簧钢条弯曲而成,其中所述横截面(62)的沿着纵向方向(30)的尺寸(64)大于其横向于所述纵向方向(30)的尺寸(66)。
10.根据前述权利要求中任一项所述的传动机构-驱动单元(10),其特征在于,所述横截面(62)的沿着纵向方向(30)的尺寸(64)大致具有和所述背部(46)的沿着纵向方向(30)的宽度(47)相同的延伸度,并且尤其所述围圈弹簧(50)的第一径向侧(51)面状地抵靠在所述楔形的构件(44)的背部(46)上的部分圆形的***(91)上。
11.根据前述权利要求中任一项所述的传动机构-驱动单元(10),其特征在于,所述轴(18)具有端侧的端面(32)或凸缘(23)来作为止挡面(35),所述轴(18)以所述凸缘经由楔形的构件(44)轴向地支撑在所述传动机构壳体(15)的配对止挡面(36)上,并且尤其轴向地在所述楔形的构件(44)与所述轴(18)的启动面(25)之间布置有单独地构造的启动盘(28)。
12.根据前述权利要求中任一项所述的传动机构-驱动单元(10),其特征在于,所述轴(18)被构造为主轴(20)并且具有螺杆齿部或者螺纹齿部(74),所述螺杆齿部或螺纹齿部尤其能够由电驱动马达(12)的输出齿部(72)来驱动。
13.根据前述权利要求中任一项所述的传动机构-驱动单元(10),其特征在于,所述楔形的构件(44)U形地构造并且包围着所述轴(18),并且尤其轴向地支撑在抗扭转地布置在轴(18)上的蜗轮(24)上。
14.根据前述权利要求中任一项所述的传动机构-驱动单元(10),其特征在于,所述预装配的单元(60)和所述传动机构壳体盖(16)能够沿着径向方向(31)来安装,并且在所述传动机构壳体盖(16)上成形有圆形的拱起(54),所述围圈弹簧(50)的第二径向侧(52)沿着径向方向(30)嵌合到所述圆形的拱起中,并且尤其在所述传动机构壳体盖(16)上模制有至少一个支承套(33),所述支承套将所述轴(18)沿着径向方向(13)朝向传动机构壳体(15)的径向的支承座(32)挤压。
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DE102021203722.4A DE102021203722A1 (de) | 2021-04-15 | 2021-04-15 | Getriebe-Antriebseinheit mit Axialspielausgleich |
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DE19854535A1 (de) | 1998-11-26 | 2000-06-15 | Valeo Auto Electric Gmbh | Antriebsvorrichtung, insbesondere für eine Scheibenwischanlage eines Kraftfahrzeugs |
DE102005045919A1 (de) | 2005-09-26 | 2007-03-29 | Robert Bosch Gmbh | Getriebe-Antriebseinheit mit Axialspielausgleich |
DE102018100458B4 (de) | 2018-01-10 | 2019-10-24 | Nidec Motors & Actuators (Germany) Gmbh | Getriebegehäuseeinheit und Getriebeeinheit mit keilförmigem Ausgleichselement zum Axialspielausgleich |
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