CN1926365A - 用于液压组件的密封件 - Google Patents
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Abstract
一种用于液压组件的密封装置,其中液压液体容纳在形成于所述组件的主体(52)和止推元件(51)之间的工作腔(53)中。所述装置包括具有相对的密封面的环形密封件(63),所述相对的密封面被推入具有收敛密封表面的所述主体(52)和止推元件(51)之间而形成密封配合。所述装置还可具有塞入腔室(53)的过行程端的压力释放阀(100)以防止环形密封件(63)过行程损伤,所述压力释放阀包括多孔主体(101),所述多孔主体允许液压液体从腔室(53)排出,并且允许环形密封件(63)不受阻碍地通过塞住的点。
Description
技术领域
本发明涉及用于液压组件的高温密封件,尤其适于液压紧固件和螺母的密封件。
背景技术
液压张力螺母、垫圈和类似的紧固件提供了一种双头螺栓或螺栓张紧的手段,这种张紧是通过液压促动螺母或垫圈对双头螺栓或螺栓上施加拉伸力来实现的。这些螺母和垫圈经常在极限压力和温度下工作。
液压螺母或类似紧固件通常受到机械地预拉伸,此后,液压施加到紧固结构内的空腔以产生液压力,该液压力施加轴向拉伸负载到与紧固件啮合的双头螺栓或螺母上。可以设置锁环,以在空腔压力解除之后保持张力。
用于液压装置的密封件一般由弹性材料制成,褚如腈橡胶或聚亚安酯。针对液压通道的这些密封的方式可以分为两种,在此称为基本机制和二次机制。密封的基本机制在液压开始施加期间起作用。随着压力的增加,弹性密封件变形并且被迫进入密封件跨接所要密封的间隙的位置,在下文中称为“挤出间隙”,以便形成二次密封。
在液压促动活塞/气缸装置中,通常随着工作压力增加,气缸壁会径向膨胀,造成与活塞和气缸之间的挤出间隙成比例的增加。液压螺母工作的限制因素是它们密封的效率。诸如高压、高温、在不利条件下的寿命限制它们的应用领域和效率。如果这些因素达到了极限,无论是超乎常规或是组合在一起,都会使通常用作密封介质的材料失效。当在压力和/或温度作用下出现密封材料进入挤出间隙的流动或移动时,故障就会发生,密封就会失效。
在极限温度/压力的应用中,例如在发电机和核能站反应堆中,严格要求密封件不因施加到例如发电机壳体或管子法兰接头的螺栓或双头螺栓上的张力损失而失效,因为这种失效会导致悲惨的灾难。美国专利US 6,494,465(Bucknell)(=国际申请PCT/AU97/00425=国际公开WO 98/00660)公开了能够在高温下工作的液压组件的液压密封件范围。这种密封件结合有能够在例如活塞和气缸之间提供低压密封的边缘,所属边缘的结构可在较高的压力下,以与斜坡成角度的基部或以嵌入凹槽中的杯形,移动过所要密封的间隙。密封件可以由弹性材料和/或薄片金属形成。
美国专利US 6,494,465的密封件已经用于许多成功的高温设备、发电和核能工业的液压张力紧固件中。然而,经验表明需要用于紧固件的不同类型的密封装置,尤其是满足特殊工作的要求。
发明内容
因此,本发明的目的是提供用于诸如紧固件的液压组件的高温密封件,所述密封件具有改进的密封特性,能够承受诸如高压和/或高温的极限因素。本发明的另一目的是提供能够在所述不利条件下达到更长寿命的密封件,或至少提供现有技术密封件的替代物。
根据本发明的一种用于液压组件的密封装置,其中液压液体容纳在形成于所述组件的主体和止推元件之间的工作腔中,该密封装置包括带有相对的密封面的环形密封件,所述相对的密封面被推入主体和止推元件之间而形成密封配合,所述主体和止推元件具有收敛密封面。
优选地,所述装置还包括保持在所述组件的主体或止推元件中的环形配合弹簧夹子,所述环形配合弹簧夹子支承环形密封件的非密封表面,以保证在主体和止推元件之间的基本密封配合。
优选地,环形密封件由一对环形密封边缘形成,所述环形密封边缘在初始低压下被推入所述组件的主体和止推元件之间而形成密封配合,该密封件其余部分在更高压力下被迫进入密封配合。
优选地,其中当密封件被放置到位时,它弹性变型,使得它朝其原始形状反弹,从而推动主体和止推元件之间的密封配合。
优选地,密封件具有圆形的合拢(heal),其在压力下滚动来保持密封配合。
在另一种形式的密封装置中设有塞入腔室的过行程端的压力释放阀以防止环形密封件过行程损伤,所述压力释放阀包括多孔主体,所述多孔主体允许液压液体从腔室泄出,并且允许环形密封件不受阻碍地通过塞入的点(tapping point)。
优选地,多孔主体由烧结金属或多孔陶瓷形成。
附图说明
为了能够完全理解本发明,现在参照附图描述优选实施例,其中:
图1是液压辅助螺母元件的剖视图;
图2是图1中的组装起来的液压螺母组件的剖视图;
图2A和2B是现有技术密封件的剖视图;
图2C-2Q是根据本发明的密封件的剖视图;
图3是安装有本发明的压力释放装置的液压螺母在处于全复位位置的剖视图;
图4是表示图3的螺母在过冲程状态的剖视图;
图5是图4螺母的局部放大图;
图6和7是变形后的现有技术密封件边缘的剖视图;
图8和9是图2F-2Q的密封件的剖视图。
具体实施方式
图1和2分别图示了在美国专利US 6,494,465中公开的现有技术的液压辅助螺母的元件和组件,包括活塞51、气缸52、锁紧环59、止推垫圈50和液压工作腔53。密封件63、64以在美国专利US 6,494,465中所述的方式、设置在活塞51和气缸52之间的封闭工组腔53中。
图2A和2B图示了普通V形的现有技术密封件63、64。图2C表示根据本发明的干涉密封件10,其响应低粘性的液压介质的慢速注射。它比现有技术的密封件63、64提供更大的灵活性,因为在密封件10被压力驱动时具有更大角度。密封件10的表面11和活塞51的表面71之间的角度稍有不同,其保证密封件10上主体12的较厚部分逆着活塞51和气缸52的表面71被驱动。这种密封结构在不需要慢速压力充填过程的应用中有效。
图2D图示了相似的结构,其中气缸52上的弹簧夹子81保证了与密封表面之间的基本密封接触。图2F与现有技术的图2A和2B的设计相似,并且具有薄密封边缘113、114,以接收初始的较低压力,因此产生了的两个密封阶段。图2H表示具有密封边缘213、214的密封件210,其工作原理相同,只是能够用薄片金属冲压而成。
图2F、2H和2G的密封件110、210和310分别形成的形状能够保证当密封件110、210和310插入工作位置时,弹力会施加到密封边缘113、114、213、214、313、314上,以便提供基本密封。二次密封动作通过增加充填压力来启动。图2G的密封件310将边缘311、314的初始低压密封与双斜面相结合,迫使备份环320进行了大部分的密封工作。在这种结构中,密封功能更象多边缘协同工作的“V-密封”。
图2E图示了密封件410,其中与活塞51的壁接触的边缘413实际上承担了所有密封工作。密封件410被制成大于由密封凹槽和活塞的限制尺寸,从而当它装配时,它具有剩余的弹力将其推向所述壁。密封件410的边缘413允许弯曲,并且允许随着由于增加充填压力造成的气缸的膨胀而移动。密封件410最好用于相当低的压力和最小的径向壁偏转角。
图2J-2Q所示的密封件是完全不同的结构,其中它们在装置中有弹性负载,使得基本密封是通过密封件试图返回到其初始位置而起作用。在图8和9中示出了这种情况,其中做成图8所示形状的密封件插入图9所示的位置,使得它被密封凹槽所迫而向内,因而被压在相邻的外气缸壁上。
基本力的选择要与条件相适应,密封件要由所需弹性的材料制成,使得它们在插入所要求的形状时产生变形。图2J-2Q所示的密封件都使用这种弹簧负载原理来实现基本密封。然后,这种密封作用通过增加气缸52的内压来加强。作用于所述壁的密封力取决于成比例地响应注射压力的密封件的面积。
在压力和温度的影响下,密封元件的薄截面的变形减小,并且经常破坏密封件的完整性。具有图2A和2B所示薄边缘的现有技术的密封件要求始终对气缸壁的保持一些弹性压力。这就意味着要选择足够屈服强度的材料,使得密封件在高局部应力的区域不发生塑性变形。如果材料的强度不足,就会产生永久变形。这种现象倾向于从较薄的截面到具有足够厚度的点渐次地发生,以平衡破坏力,因此当密封边缘以这种方式变形时,它会从与气缸壁的接触状态弯曲回来。
升高的温度降低多数材料的有效强度,特别是工程钢的有效强度,使用中发生了变形的金属密封件难以恢复使用。在压力作用下介质强制进入在薄边缘处形成的间隙,并且像楔子一样起作用,从而迫使下部截面与气缸壁脱离密封接触。图6和7示出了现有密封件的这个问题。
图2J-2Q的“密封环”式密封件的创造性的设计,通过充填液体的压力对所述密封的相对表面的作用解决了这个问题,其产生推力来帮助临界面的密封。这种力直接涉及增加的压力,因此,保持了密封整个范围需要的关系。通过具有厚截面区域的新设计,解决热量影响薄截面并且造成永久变形的问题。
在图2J、2K和2N中示出了具有这些特性的密封件510、610和710。图2L和2M所示的密封件810和910表示了图2J和2K的密封件510和610的中空变型,但是,一般在实际应用上有限制。图2O和2Q的密封件910、1010示出了“弹簧圈”的原理是如何能够用于较薄截面的材料。这些都能够便宜地制作,并且一般对于在较低工作压力下使用的液压辅助螺母紧固件足够了。密封件110或图2P示出了能够做成V字形的密封件的形式,其中压力作用膨胀密封件的外径并且提供与气缸52的壁的密封。
对本领域的技术人员来说,显而易见,密封件的材料选择,密封件的具体形状、尺寸和结构取决于应用意图。选择合适密封件的重要因素包括液压组件的工作温度和压力、充填介质的类型和压力。
破坏密封件整体性的另一个因素是超行程,即,在试图操作期间,密封件移动超出它实际工作极限,导致了故障和高压液体的危险喷发。为了防止这种故障,理想的是,将溢流口引入液压辅助紧固件螺母。如果密封件被迫移动超过其行程极限,那么该端口会通过使液体溢出来减小对密封件的损害。然而,密封件甚至会因局部通过所述溢流口而受到不可恢复的损坏,因为极大的压力会在密封件通过时将密封件材料挤出,甚至刮伤坚硬的钢表面。
图3-6图示了容纳有压力释放装置的排液端口100,其包括多孔塞101。塞101的内表面在轮廓上与相邻的密封壁表面52A向吻合,使得当密封件63移过排液端口100时不会受到损伤。多孔塞101的材料选择为具有高强度,以当密封件63移过排液端口100时对其提供支撑,并且多孔塞的材料是多孔的,以允许液体103从压力腔53自由地流出。随着密封件63在排液端口100上的移动,多孔塞101的更多材料暴露出来,使得排液率增大。选择塞101的密度和相应的多孔性,以便为应用提供合适的强度和排液率。为塞101选择的低成本材料是烧结金属和多孔陶瓷,但是,其它材料也适合。
对本领域的技术人员来说,显而易见,如果密封件从图3所示的全复位位置移到图4所示过行程状态,压力释放装置的多孔塞101会保护密封件63免于受到损坏。本发明的多孔排液塞能够应用于会对密封件产生过行程损伤的任何液压组件。
应该认识到,上面的描述仅通过图示的实例给出,对本领域的普通技术人员来说是显而易见的所有其它变型和变化都被认为落入在此阐述的本发明的宽泛范围和界限内。在本说明的整个说明书和权利要求书中,词“包括(comprise)”和这个词的变型,诸如“comprises”和“comprising”不排除其它的附加元件整体或步骤。
Claims (7)
1.一种用于液压组件的密封装置,其中液压液体被容纳在形成于所述组件的主体和止推元件之间的工作腔中,所述组件包括具有相对的密封表面的环形密封件,所述相对的密封表面被推入具有收敛密封表面的主体和止推元件之间而形成密封配合。
2.如权利要求1所述的密封装置,其还包括保持在所述组件的主体或止推元件中的环形配合弹簧夹子,所述环形配合弹簧夹子支承所述环形密封件的非密封面,以保证在主体和止推元件之间的基本密封配合。
3.如权利要求1所述的密封装置,其中环形密封件形成有一对环形密封边缘,所述环形密封边缘在初始低压下被推入所述组件的主体和止推元件之间而形成密封配合,密封件的其余部分在更高压力下形成密封配合。
4.如权利要求1所述的密封装置,其中密封件在被放置到位时受到弹性负载,因而试图返回到原始形状,从而迫使所述主体和止推元件之间形成密封配合。
5.如权利要求1所述的密封装置,其中所述密封件具有圆形的合拢,其在压力下滚动以保持密封配合。
6.如权利要求1所述的密封装置,其设有塞入腔室的过行程端的压力释放阀以防止环形密封件受到过行程损伤,所述压力释放阀包括多孔主体,所述多孔主体允许液压液体从腔室排出,并且允许环形密封件不受阻碍地通过塞住的点。
7.如权利要求5所述的密封装置,其中多孔主体由烧结金属或多孔陶瓷形成。
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2004900922 | 2004-02-25 | ||
AU2004900922A AU2004900922A0 (en) | 2004-02-25 | High temperature seals for hydraulic assemblies |
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CN1926365A true CN1926365A (zh) | 2007-03-07 |
CN100404924C CN100404924C (zh) | 2008-07-23 |
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CNB2005800060069A Active CN100404924C (zh) | 2004-02-25 | 2005-02-25 | 用于液压组件的密封件 |
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US (2) | US20110068543A1 (zh) |
EP (1) | EP1718890B1 (zh) |
JP (1) | JP4739320B2 (zh) |
CN (1) | CN100404924C (zh) |
AU (1) | AU2005214453B2 (zh) |
ES (1) | ES2556110T3 (zh) |
WO (1) | WO2005080837A1 (zh) |
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- 2005-02-25 JP JP2007500007A patent/JP4739320B2/ja active Active
- 2005-02-25 AU AU2005214453A patent/AU2005214453B2/en active Active
- 2005-02-25 EP EP05706289.5A patent/EP1718890B1/en active Active
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2012
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JP2007524049A (ja) | 2007-08-23 |
CN100404924C (zh) | 2008-07-23 |
EP1718890A4 (en) | 2012-03-14 |
AU2005214453A1 (en) | 2005-09-01 |
JP4739320B2 (ja) | 2011-08-03 |
US20110068543A1 (en) | 2011-03-24 |
US9816614B2 (en) | 2017-11-14 |
US20130220450A1 (en) | 2013-08-29 |
EP1718890A1 (en) | 2006-11-08 |
ES2556110T3 (es) | 2016-01-13 |
EP1718890B1 (en) | 2015-09-16 |
AU2005214453B2 (en) | 2009-07-16 |
WO2005080837A1 (en) | 2005-09-01 |
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