CN117515020A - 具有滚动元件的轴承单元 - Google Patents
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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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/62—Selection of substances
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- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
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- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
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- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
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- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
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- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
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- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
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Abstract
一种具有滚动元件的轴承单元(30),其容纳在壳体(10)的径向内部的安装座部(11)中,轴承单元具有:径向外且固定的涂覆圈(50),设置有金属环(31)和由弹性体材料制成的衬套(40),衬套与金属环的径向外表面(31a)一体化;径向内圈(33),能够相对于旋转轴线(X)旋转;成列滚动元件(32),介于涂覆圈(50)与径向内圈(33)之间;衬套的弹性体材料是硫化热塑性材料;衬套(40)共成型到金属环(31)的径向外表面(31a)上并且包括圆柱形主体(41)和至少两个环形突起(42),至少两个环形突起(42)装配在形成在金属环(31)的表面(31a)上的相应锚固槽(31c)内。
Description
技术领域
本发明涉及一种具有滚动元件的轴承单元。
背景技术
已知类型的轴承单元通常设置有:径向外圈,固定到(fixed to)固定元件(/静止元件)(stationary element)(例如,框架);径向内圈,用于支撑旋转元件(例如,旋转轴);以及多个滚动元件,介于两个圈之间,以允许两个圈的相对旋转。
上述已知类型的轴承单元用在各种工业应用中,并且下面的描述将具体提及这些轴承单元在加热、通风和空调系统中(即,在环境调节系统中)的使用以及轴承单元安装在所述系统的风扇中以允许支撑叶轮(impellers)的相关旋转轴旋转的情况,而不会失去轴承单元的一般特征。
这些环境调节系统又广泛用在土木工程领域(例如,用于摩天大楼或大型机场中的空调)以及航空、机动汽车和铁路工业中,并且所有这些领域的主要挑战之一是降低振动水平和噪声水平。
过度的振动水平导致较高的能量消耗,并且可能导致过早故障(/失效)(failure),从而导致非程序化的停机时间以进行维护,并导致产量的下降。高的噪声水平又导致工作人员的不健康工作环境。
因此,为了降低由旋转轴产生的且经由轴承单元在框架中引起的振动,并尽可能地限制随后的噪声水平,并且还尽可能地限制这些振动可能对所述轴承单元造成的任何损坏,轴承单元还包括弹性体材料的环(/圈)(ring),该环介于在轴承单元的外圈与用于将所述轴承单元安装在框架中的座部(seat)之间,并且通常装配到外圈的外表面上。
上述类型的轴承单元虽然以一些方式管理而降低了振动水平和噪声水平,但是在安装和可靠性方面都存在若干问题和缺点,因为衬于(/垫在)(lines)轴承的金属外圈的弹性体材料环通常在将轴承单元组装在相应的座部中的过程中趋于(/倾向于)(tends to)撕裂(/撕碎)(tear)和损坏,此外,在使用期间还趋于变得相对于外圈不对准(/错位)(misaligned)。实际上,为了避免必须制造具有较大尺寸的轴承单元的安装座部(mountingseat),尝试尽可能地(使安装座部)容纳弹性体材料环的径向厚度,然而,这不但损害了弹性体材料环的机械强度,而且损害了弹性体材料环的稳定性,特别是当本申请的旋转轴的旋转速度非常高(这是上述系统的典型情况)时。
发明内容
本发明的目的是提供一种具有滚动元件的轴承单元,其不仅能够以简单且低成本的方式解决上述缺点,而且还有助于进一步提高降低振动水平和噪声水平的能力。
根据本发明,提供一种具有在所附权利要求中描述的特征的具有滚动元件的轴承单元。
附图说明
现在将参照示出了本发明的实施方式的一些非限制性示例的附图来描述本发明,在附图中:
图1示出了根据本发明的一个优选实施方式的具有滚动元件的轴承单元的截面图;
图2以较大比例和截面示出了根据图1的轴承单元的细节;
图3示出了根据图1的轴承单元的截面图,并且示出了其中容纳轴承单元的壳体(/轴承座)(casing);以及
图4以较大比例和截面示出了根据图1的轴承单元的进一步细节。
具体实施方式
下面仅以示例的方式描述根据本发明的具有滚动元件的轴承单元的实施方式的优选示例。
参照图1,30表示根据本发明的轴承单元的一个优选实施方式整体,其中,轴承单元30有利地但不是一定用在通风系统工业中。
轴承单元30被设计成容纳在壳体(/轴承座)(casing)10的径向内部的安装座部11(在图1中仅部分地示出)内,并且包括:
-径向外且固定的(/静止的)(stationary)涂覆圈(coated ring)50;
-径向内圈33,能绕着轴承单元30的中心旋转轴线X旋转;
-成列滚动元件32,在本示例中为球,介于涂覆圈50与径向内圈33之间;
-保持架34,用于容纳(containing)滚动元件,使得将滚动元件32列中的滚动元件保持就位;
-一对密封部件35,配置在该滚动元件32列的相对侧(/两侧)(opposite sides),以使轴承单元与外部环境密封隔离(seal off)。
在整个本说明书和权利要求书中,指示位置和取向的术语和表述(诸如,“径向”和“轴向”)参照轴承单元30的中心旋转轴线X来理解。
为了简化图示起见,附图标记32将归属为单个球和球列(/球的列)两者。同样为了简单起见,在本说明书和附图中,可以以示例的方式使用术语“球”来代替更通用的术语“滚动元件”(同样将使用相同的附图标记)。实施方式的一些示例和相关附图可以设想使用除球之外的滚动元件(例如,滚子),而不会脱离本发明的范围。
根据本发明并且还参照图2,轴承单元30的径向外涂覆圈50包括金属环31和弹性体材料的衬套(/衬/衬里/内衬)(liner)40,弹性体材料的衬套40与金属环31一起共成型(co-moulded),并且绕着金属环31的径向外表面31a配置。因此,衬套40在径向上相对于金属环31位于外部,并且与金属环31一起形成单个组成部件(径向外涂覆圈50),该单个组成部件将容纳在壳体10的安装座部11内。
衬套40的弹性体材料是硫化热塑性材料(TPE),硫化热塑性材料具有良好的耐疲劳性和耐剪切力特性,并且鉴于其在室温下恢复到其原始形状的趋势,在经受压缩时具有良好的弹性行为。
在测试条件下验证了这两个特性:
-借助于破裂测试(rupture test)。在这些测试中,当TPE衬套40在与径向外圈上的支撑表面(所述表面是“橡胶与金属”接触的表面)平行的平面中受到水平力时,TPE衬套40没有显示出裂纹(/裂痕/裂缝)(fractures)或撕裂(tearing)的迹象;
-借助于高温动态疲劳测试。当TPE衬套40受到各个方向上且不同强度的载荷(例如,端部上的推力(thrusts))时,由于弹性效应,抑制了中央部分上的振动,因此,中央部分上的变形的影响受到限制。
因此,利用其中衬套40共成型到径向外圈上并且由TPE制成的本解决方案,弹性体衬套的厚度可以减小到最小。实际上,由于衬套40是共成型的并因此牢固地紧固到金属环31上,并且还由具有良好弹性行为的耐断裂材料制成,因此衬套40可以具有非常小的径向厚度,而没有在安装期间损害其完好状态的风险。此外,在需要较大直径或需要尺寸大于国际标准(ISO、JIS等)中规定的尺寸的壳体(casing)的情况下,对于衬套40使用较小厚度不会影响壳体10中的安装座部11的选择。
如下面将更清楚地看到的,衬套40具有保持在金属环31的轴向尺寸内的轴向尺寸,从而不会改变轴承单元30的最大轴向体积,并且在必要时,允许金属环31的环形端表面31b用作安装有轴承单元30的其他组成部件的接触和/或定位表面。
衬套(liner)40包括圆柱形主体41和两个环形突出部42,两个环形突出部42在径向上相对于圆柱形主体41位于内部,并且位于相对于轴承单元30的径向对称轴线Y的相对侧。由于硫化热塑性材料的填充锚固槽的最佳能力,在共成型期间,这些环形突出部42将形成在相应的锚固槽31c内,锚固槽31c形成在金属环31的表面31a上并且也相对于径向轴线Y对称。
在共成型工艺期间,衬套40的环形突出部42与金属环31的相应锚固槽31c的组合(/套组)(set)使得金属环31和衬套40紧固在一起并将这两个组成部件固定在一起,以形成径向外涂覆圈(radially outer coated ring)50。
环形突出部42的数量和相应的锚固槽31c的数量必须至少为两个,以能够确保两个共成型的组成部件牢固地紧固在一起。显然,包括多于两个的多个环形突出部42和相应的锚固槽31c的实施方式将是可行的,而不会脱离本发明的精神。
可以理解的是,为了确保这种新的涂覆圈50的最佳性能,为这种解决方案配备优化的尺寸是有利的。
还参照图3和图4,衬套40的轴向尺寸A(即,衬套40的两个环形端表面43之间的距离)小于金属环31的轴向尺寸B(即,金属环31的两个环形端表面31b之间的距离),使得:
A=B-2mm
如已经提到的,这是为了不改变轴承单元30的最大轴向体积,并且在必要时,能够使用金属环31的环形端表面31b作为用于其中安装有轴承单元30的其他组成部件的接触和/或定位表面。此外,鉴于轴向距离B与轴向距离A之间的两毫米的差,结果是衬套40覆盖金属环31的整个圆柱形表面31a,然而,在存在连接表面31d(即,将圆柱形表面31a连接到环形端表面31b的那些)的区域中,(衬套40)不会突出超出该圆柱形表面31a,以避免形成弹性体在金属上的非最佳粘附区域。
同样重要的是正确限定衬套40的厚度T,更确切地,正确限定衬套40的圆柱形主体41在未变形状态(即,衬套40尚未组装在容纳壳体10中的状态)下的厚度。该厚度的值太高将不利于轴承单元30(并因此不利于其容纳壳体10)的径向体积。另一方面,厚度T的值太低将无助于以最佳方式衰减噪声水平和振动水平。通过将TPE材料用于衬套40,可以在模拟(/仿真)以及上述实验测试之后限定圆柱形主体41的厚度T的值的最佳范围,该范围在0.45mm与0.55mm之间。
金属环31和衬套40的正确紧固在一起还是确保所获得的新组成部件(即,径向外涂覆圈50)的稳定性的基础。因此,锚固槽31c的数量和尺寸必须与衬套40的圆柱形主体41的厚度T相关:厚度T越大,锚固槽31c的数量和/或宽度(轴向E和径向C)越大,以容纳更多的弹性体材料(环形突出部42),从而确保最佳紧固。这些参数之间的最佳关系如下:
·锚固槽31c的数量n:n=2
·锚固槽31c的轴向宽度E:E=2×T
·锚固槽31c的径向宽度C:C=2×T
因此,两个尺寸(径向宽度C和轴向宽度E)以成正比(directly proportional)的方式与衬套40的圆柱形主体41的厚度相关:通过这样做,随着圆柱形主体的厚度的增大,锚固槽的深度(径向宽度C)和宽度(轴向宽度E)成比例地增大,以保持衬套40的圆柱形主体41牢固地紧固到金属环31。基于测试结果估计比例因子为2。
此外,为了将径向外涂覆圈50正确插入壳体10内,圆柱形主体41的端部41'(即,在突出部42的外侧在轴向上延伸的那些部分)必须不存在任何分离。为此目的,端部41'的轴向尺寸F优选必须不超过锚固槽31c的轴向宽度E的一半,即:
F<E/2
轴承单元30(即涂覆圈50)在壳体10的安装座部11中的安装借助于过盈配合(/干涉配合)(interference fit)来执行,并且在安装期间,弹性体材料将经受压缩变形(compression crushing)。同样取决于预选的弹性体材料,重要的是限定弹性体的压缩变形,使得一方面它不会过度,导致不利地影响所述衬套的功能,并且另一方面它不会太小,从而确保轴承单元30与壳体10之间的正确过盈(correct interference)。如果压缩变形(compression crushing)w被定义为相对于圆柱形主体41的初始未变形厚度T计算的圆柱形主体41由于安装在壳体10中而经历的厚度的减小,则成品元件的模拟分析和随后的实验确认测试已经表明,该变形w通过以下关系与衬套40和金属环31的圆柱形表面31a的其他几何参数相关:
w=[(B-A)×T]/B
其中,如上所述,A是衬套40的轴向尺寸,B是金属环31的轴向尺寸,并且T是圆柱形主体41在未变形状态下的厚度。
这种关系源于申请人的考虑,同样基于申请人的经验,即弹性体材料或多或少是不可压缩的,即当“变形(crushed)”时,弹性体材料倾向于保持相同的体积。因此,被压缩的弹性体部分必须能够“填充”“自由”空间(在轴线Y的相对侧在轴向上位于外部),一旦壳体10和金属环31被组装,就在壳体10与金属环31之间产生“自由”空间。
因此,如果弹性体衬套没有足够的自由空间来在轴向上膨胀,则可以避免:
-引入作用在径向外圈上的附加应力,在最坏的情况下,导致滚道变形和轴承单元的工作寿命缩短;
-构成弹性体的元素(特别是混合物的液体成分)渗漏(seepage)的风险。
已知弹性体材料的压缩变形w,可以限定径向外涂覆圈50与壳体10之间的安装关系。特别地,该关系将使涂覆圈50的外径d(即,涂覆圈50的径向外圆柱形表面51的直径d)与壳体10的内径D(即,壳体10的径向内安装座部11的直径D)相关联,并且将是:
d=D+2w
其中,如上定义的,w是衬套40的压缩变形。
基本上,本发明提供了一系列优点可以总结如下:
-径向外圈的弹性体材料衬套的存在降低了噪声水平和振动水平,特别是在通风系统(或其他机械)的高速下;
-此外,它改善了轴承单元与通风系统的框架的对准。以这种方式,可以减小作用在单个轴承单元上的力,并且降低随后的噪声水平和振动水平;
-共成型到径向外圈上的弹性体衬套的设计允许减小轴承单元的径向体积;
-利用该解决方案的设计,可以获得单个组成部件(径向外涂覆圈),而不是两个单独的组成部件。
除了如上所述的本发明的实施方式之外,应理解,存在许多另外的变型。还必须理解,所述实施方式仅是示例,并且既不限制本发明的范围,也不限制其应用,也不限制其可行构造。相比之下,尽管上面提供的描述使得本领域技术人员能够至少以其构造示例中的一个示例实现本发明,但是必须理解,所描述的组成部件的许多变型是可行的,而不会因此脱离如所附权利要求中限定的按照字面(/文字)上解释的和/或根据其法律等同物解释的本发明的范围。
Claims (9)
1.一种轴承单元(30),具有容纳在壳体(10)的径向内部的安装座部(11)中的滚动元件,所述轴承单元(30)包括:
-径向外且固定的涂覆圈(50),设置有金属环(31)和由弹性体材料制成的衬套(40),所述衬套(40)与所述金属环(31)的径向外表面(31a)一体化;
-径向内圈(33),能够相对于旋转轴线(X)旋转;
-成列滚动元件(32),介于所述涂覆圈(50)与所述径向内圈(33)之间;
所述轴承单元(30)的特征在于:
-所述衬套(40)的弹性体材料是硫化热塑性材料;
-所述衬套(40)共成型到所述金属环(31)的径向外表面(31a)上,并且包括圆柱形主体(41)和至少两个环形突出部(42),所述至少两个环形突出部(42)装配在形成在所述金属环(31)的表面(31a)上的相应锚固槽(31c)内。
2.根据权利要求1所述的轴承单元(30),其特征在于,所述环形突出部(42)在径向上相对于所述圆柱形主体(41)位于内部,并且相对于所述轴承单元(30)的径向对称轴线(Y)位于相对侧。
3.根据权利要求2所述的轴承单元(30),其特征在于,所述衬套(40)的轴向宽度(A)小于所述金属环(31)的轴向宽度(B)。
4.根据权利要求2或3所述的轴承单元(30),其特征在于,所述衬套(40)的圆柱形主体(41)的厚度(T)在0.45mm与0.55mm之间的范围。
5.根据权利要求4所述的轴承单元(30),其特征在于,所述两个锚固槽(31c)的径向宽度(C)等于所述圆柱形主体(41)的厚度(T)的两倍。
6.根据权利要求4或5所述的轴承单元(30),其特征在于,所述两个锚固槽(31c)的轴向宽度(E)等于所述圆柱形主体(41)的厚度(T)的两倍。
7.根据权利要求6所述的轴承单元(30),其特征在于,所述圆柱形主体(41)的端部(41')的轴向宽度(F)不超过所述锚固槽(31c)的轴向宽度(E)的一半。
8.根据权利要求4至7中任一项所述的轴承单元(30),其特征在于,在所述壳体(10)内的安装操作构造中,所述圆柱形主体(41)的压缩变形(w)等于:
w=[(B-A)×T]/B。
9.根据权利要求8所述的轴承单元(30),其特征在于,径向外的所述涂覆圈(50)的外径(d)等于:所述壳体(10)的安装座部(11)的内径(D)增加两倍的所述圆柱形主体(41)的压缩变形(w)。
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