CN103362641A - 涡轮增压器旋转组件中的平衡漂移的控制 - Google Patents
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Abstract
一种内燃机用涡轮增压器,其包括具有轴承孔和止推墙的轴承壳体。轴承壳体包括布置在孔中的轴颈轴承。涡轮增压器还包括由轴颈轴承支撑的轴,以在孔内绕轴线旋转。涡轮增压器还包括固定至轴的涡轮叶轮,且该涡轮叶轮配置为通过发动机排出的燃烧后气体绕轴线旋转。涡轮增压器附加地包括压缩机轮,其固定至轴且配置为对周围环境空气流加压。此外,涡轮增压器包括受压在轴上且配置为传输由涡轮叶轮产生的推力至止推墙的止推轴承组件。将止推轴承组件压在轴上使得止推轴承组件和轴之间的径向运动最小化。还公开了一种包括该涡轮增压器的内燃发动机。
Description
技术领域
本公开涉及在涡轮增压器的旋转组件中控制平衡漂移。
背景技术
内燃发动机(ICE)通常被用于在可靠的基础上长时间地产生高水平的功率。许多这种ICE组件采用增压装置(诸如排气涡轮驱动涡轮增压器)来在气流进入发动机的进气总管之前压缩气流,以增加功率和效率。
具体地,涡轮增压器是和通过周围环境大气压力相比迫使更多空气继而迫使更多氧气进入ICE的燃烧室中的离心气体压缩机。强迫进入ICE中附加质量的含有氧气的空气改进了发动机的体积效率,允许其在给定的循环中燃烧更多的燃料,并由此产生更多的功率。
常见的涡轮增压器采用由一个或多个轴承支撑的中心轴,且在排气驱动涡轮叶轮和空气压缩机轮之间传输旋转运动。涡轮和增压机轮两者都固定至轴,其和各个轴承构件一起构成涡轮增压器旋转组件。由于旋转组件经常以超过每分钟100000转(100000RPM)的速度旋转,这样的组件的平衡对于涡轮增压器的长时间的耐用性来说是必需的。
发明内容
本公开的一个实施例涉及内燃机用涡轮增压器,其包括具有轴承孔和止推墙的轴承壳体。轴承壳体包括布置在孔中的轴颈轴承。涡轮增压器还包括具有第一端部和第二端部的轴,该轴由轴颈轴承支撑,以在孔内绕轴线旋转。涡轮增压器还包括固定至轴且靠近第一端部的涡轮叶轮,且该涡轮叶轮配置为通过发动机排出的燃烧后气体绕轴线旋转。涡轮增压器还附加地包括固定至轴且靠近第二端部的压缩机叶轮,且该压缩机叶轮配置为对接收自周围环境的空气流加压,以传输至发动机。此外,涡轮增压器包括受压在轴上且配置为传输由涡轮叶轮产生的推力至止推墙的止推轴承组件。将止推轴承组件压在轴上使得止推轴承组件和轴之间的径向运动最小化。
轴可包括轴肩。在这样的情形中,压缩机叶轮可经由紧固件(诸如锁紧螺母)保持在轴上,且随着紧固件被拧紧,压缩机轮可被压靠止推轴承组件且止推轴承组件被压靠轴肩。
止推轴承组件可包括止推环和止推垫圈。止推垫圈可配置为随着紧固件被拧紧而把止推环压靠轴肩。
发动机油被引导润滑止推轴承组件,并在止推垫圈和止推墙之间产生油膜。
止推轴承组件压在轴上可在止推轴承组件和轴之间产生范围在约5-15μm的过盈配合。
压缩机轮可压在轴上。压缩机叶轮压在轴上可在压缩机叶轮和轴之间产生范围在约25-30μm之间的过盈配合。
止推轴承组件可沿轴线布置在轴上,在轴颈轴承和压缩机叶轮之间。
本公开的另一实施例涉及一种包括上述的涡轮增压器的内燃发动机。
当结合附图以及所附的权利要求时,本发明的上述特征和优势以及其他特征和优势从下文中用于实施描述的发明的(一个或多个)最佳模式和(一个或多个)实施例的详尽描述中是轻易地明显的。
附图说明
图1是具有根据本公开的涡轮增压器的发动机的示意性透视图。
图2是图1中示出的涡轮增压器的示意性横截面视图,其中涡轮增压器包括支撑涡轮增压器旋转轴的轴承壳体。
图3是图2中示出的轴承壳体的示意性放大局部横截面视图,特别示出了压在轴上的止推轴承组件和压缩机轮。
具体实施方式
参见附图,其中相同的附图标记在若干幅附图中对应相同或相似的构件,图1示出了内燃发动机10。发动机10包括汽缸缸体12,其具有多个汽缸14布置在其中。如所示,发动机10还包括汽缸盖16。每一个汽缸14包括配置为在其中往复运动的活塞18。燃烧室20形成为在汽缸14中,在汽缸盖18的底表面和活塞18的顶部之间。如本领域技术人员已知的,燃烧室20配置为接收燃料-空气混合物,用于其中的后续燃烧。
发动机10还包括配置为在汽缸缸体12中旋转的曲轴22。由于在燃烧室20中恰当比例的燃料-空气混合物燃烧,曲轴22通过活塞18旋转。在燃料-空气混合物在特定的燃烧室20中燃烧后,特定活塞18的往复运动用于将燃烧后气体24从相应的汽缸14排出。发动机10还包括机油泵26。机油泵26配置为供应受压发动机油28至各个轴承,诸如曲轴22的轴承。机油泵26可由发动机10直接地驱动,或由电动机(未示出)驱动。
发动机10附加地包括进气系统30,其配置为将气流31从周围环境引导至汽缸14。进气系统30包括进气管32、涡轮增压器34和进气总管36。尽管未示出,进气系统30可附加地包括位于涡轮增压器34上游的空气过滤器,以从气流31中移除外来微粒和其他空气携带的碎屑。进气管32配置为将气流31从周围环境引导至涡轮增压器34,而涡轮增压器配置为对接收的气流加压,且排出受压的气流至进气总管36。进气总管36继而将此前受压的气流31分配至汽缸14,以和恰当量的燃料混合,且用于产生的燃料-气体混合物的后续燃烧。
如在图2中所示,涡轮增压器34包括具有第一端部40和第二端部42的钢轴38。涡轮叶轮46安装在轴38上,靠近第一端部40,且配置为通过从汽缸14排出的燃烧后气体24而和轴38一起绕轴线43旋转。涡轮叶轮46通常由温度和氧化耐受材料制成,诸如镍铬基“因科内尔(inconel)”超级合金,以可靠地耐受燃烧后气体24的温度,该温度在一些发动机中可达到2000华氏度。涡轮叶轮46布置在包括涡螺或卷状物50的涡轮壳体48中。卷状物50接收燃烧后排气24,且引导排气至涡轮叶轮46。卷状物50配置为实现特定的性能特质,诸如涡轮增压器34的效率和响应。
如在图2中进一步示出的,涡轮增压器34还包括在第一端部和第二端部40、42之间安装在轴38上的压缩机轮52。压缩机轮52经由特殊构造的紧固件(诸如锁紧螺母53)而保持在轴38上。如本领域人所理解的,锁紧螺母53是包括夹紧或不相等螺距内螺纹以接合匹配构件(例如轴38)的外螺纹的紧固件类型。锁紧螺母53的这样的螺纹构造用于最小化锁紧螺母在涡轮增压器34的运行期间从轴38松开的可能性。附加地,锁紧螺母53上螺纹的方向可选择为使得锁紧螺母在轴38由燃烧后气体24旋转加速时将具有拧紧的趋势而不是松开。
压缩机轮52被配置为对从周围环境接收的气流31加压,用于最终输送至汽缸14。压缩机叶轮52布置在包括涡螺或卷状物56的压缩机壳体54中。卷状物56接收气流31并将气流引导至压缩机叶轮52。卷状物56配置为实现特定的性能特质,诸如涡轮增压器34的峰值气流和效率。相应地,旋转被给涡轮叶轮46供能的燃烧后排气24赋予轴38,且继而传输至压缩机轮52,这是由于压缩机轮被固定至轴。如本领域技术人员所理解的,燃烧后排气24的变动的流量和力影响了可由压缩机轮52在发动机10的操作范围中产生的增压的量。压缩机轮52通常由高强度铝合金制成,其向压缩机轮提供降低的旋转惯量和更快的旋转加速响应。
继续参照图2,轴38被经由轴颈轴承58支撑以绕轴线43旋转。轴颈轴承58安装在轴承壳体62的孔60中,且被经由泵26供应的受压的发动机油28的供应润滑且冷却。轴承壳体62包括止推墙64。轴承壳体62可由诸如铁的硬材料制成,以在涡轮增压器34的操作期间向孔60提供在升高的温度和载荷下的尺寸稳定性。轴颈轴承58配置为控制轴38的径向运动和振动。如所示,轴颈轴承58可为完全浮动或半浮动类型,其由相对软的金属制成(诸如青铜或黄铜),使得通过轴承系统的任意碎屑将嵌入在软轴承材料中,且不损坏轴38或孔60。轴颈轴承58还可配置为滚珠或球轴承,以进一步降低轴38的旋转期间的涡轮增压器摩擦力损失。
如在图2中所示,涡轮增压器34还包括止推轴承组件66。止推轴承组件66可包括止推环70和止推垫圈72。涡轮增压器34还包括止推板71,其由止推保持器73抵靠承载壁64保持在位。止推板71的轴承表面通常由相对软的金属制成(诸如青铜或黄铜),使得通过轴承系统的任意碎屑将嵌入在软轴承材料中,且不损坏止推环70或止推垫圈72。止推保持器73可由夹子、一个或多个螺栓保持在位,或以其他方式附连至壳体62,以保持止推轴承组件66牢固地抵靠承载壁64。
止推轴承组件66抵消在涡轮增压器34中产生的净推力,当这样的力朝向压缩机轮52作用时。尽管未示出,止推轴承组件66可附加地包括布置在压缩机轮52的侧部上的附加的止推垫圈,以及其他构造,如本领域技术人员所理解的。如所示,止推轴承组件66沿轴线43布置在轴38上,在轴颈轴承58和压缩机轮52之间,且被压在轴上。轴承组件66被经由泵26供应的受压的发动机油28的供应润滑且冷却。在涡轮增压器34的操作期间,即,当涡轮叶轮46被燃烧后气体24供能时,止推垫圈72传输由涡轮叶轮产生的推力至止推板71。被压在轴38上的轴承组件66用于最小化在止推轴承组件和轴之间的径向运动。
如图3所示,轴38包括轴肩68。在涡轮增压器34的装配中,随着锁紧螺母53拧紧在轴38上,压缩机轮52被推送抵靠止推轴承组件66,且止推轴承组件被推送抵靠轴肩68。相应地,锁紧螺母53的拧紧在压缩机轮52和轴肩68之间的挤压止推轴承组件66。
在止推轴承组件66至轴38上的装配期间,止推环70配置为随着锁紧螺母53被拧紧而推送止推垫圈72抵靠轴肩68。在涡轮增压器34的操作期间,来自泵26的受压的发动机油28被输送至轴承壳体62,且被引导用于润滑止推轴承组件66,以及在止推垫圈72和止推板71之间产生油膜。该油膜用于降低在止推垫圈72和止推板71之间的直接物理接触的可能性。继而,止推垫圈72和止推板71之间的这种直接接触的降低用于延长止推轴承组件66的有效寿命以及涡轮增压器34的耐久性。
如图3所示,为了在位于止推这构成组件66和轴38之间的界面处产生连续的油膜或紧接触,止推垫圈70和止推环70的内直径以及轴38的外直径可被尺寸设定为在由区域74大致以阴影示出的匹配构件之间产生过盈配合。止推环70和轴38之间、以及止推垫圈72和轴38之间的过盈配合74可例如处在大致5-15μm的范围中。该过盈配合范围很可能足以在止推环70、止推垫圈72和轴38在涡轮增压器34的操作期间(诸如在轴承壳体62内可能遇到的温度极值之间)膨胀和收缩时保持希望的牢固接触。
如图3附加地所示,压缩机轮52也可被压在轴38上。压缩机轮52的内部直径可被选择为使得由区域76大致以阴影示出的过盈配合产生在压缩机轮和轴38的外部直径之间。压缩机叶轮52和轴38之间的过盈配合76可例如处在大致25-30μm的范围中。这样的位于压缩机轮52和轴38之间的过盈配合通常大于止推轴承组件66和轴的过盈配合,这是因为铝合金具有较钢更大的热膨胀系数,且其通常用于止推环70和止推垫圈72。附加地,压缩机轮52具有比止推轴承组件66大的外部直径,且由此,压缩机叶轮的外部直径通常产生更大的膨胀,这是由于在涡轮增压器30的操作期间受到离心力。
上述在止推轴承组件66和轴38之间的过盈配合76,以及在压缩机轮52和轴之间的过盈配合是希望获得的,以由此限制轴承组件以及压缩机轮相对于轴的径向运动。该径向运动通常是不希望的,因为其可导致平衡漂移、动态不稳定、转子振动、噪声、以及轴颈轴承58的可能的过载。
通过继续参照图2,轴颈轴承62包括排油体积78,用于从泵26供应至轴承壳体的发动机油。排油体积78是包括在轴承壳体62中的内部储油器,其接收通过轴颈轴承58以及止推轴承组件66的油。如图1所示,在止推轴承组件66的润滑以及排油体积78内的机油积聚之后,排放通道80将机油从轴承壳体62移除。如图1中附加地示出的,排放通道80和泵26流体连通,以将来自排油空间78的油返回泵。
该详尽的描述和附图或图表仅用于支持和描述本发明,但本发明的范围应仅由权利要求书限定。尽管已经描述了用于执行所公开的发明的最佳模式,存在有各种可替换设计和实施例用于实施由所附的权利要求书限定的本发明。
Claims (10)
1.一种用于内燃发动机的涡轮增压器,该涡轮增压器包括:
轴承壳体,其包括轴承孔和止推墙;
轴颈轴承,其布置在孔内;
轴,其具有第一端部和第二端部,该轴由轴颈轴承支撑,以在孔内绕轴线旋转;
涡轮叶轮,其固定至轴且靠近第一端部,且配置为通过发动机排出的燃烧后气体绕轴线旋转;
压缩机轮,其固定至轴且靠近第二端部,且配置为对从周围环境接收的气流加压,以输送至发动机;和
止推轴承组件,其被压在轴上且配置为传输由涡轮叶轮产生的推力至止推墙;
其中将止推轴承组件压在轴上使得在涡轮增压器的操作期间止推轴承组件和轴之间的径向运动最小化。
2.如权利要求1所述的涡轮增压器,其中轴包括轴肩,压缩机轮经由紧固件保持在轴上,且其中随着紧固件被拧紧,压缩机轮被压靠止推轴承组件且止推轴承组件被压靠轴肩。
3.如权利要求2所述的涡轮增压器,其中止推轴承组件包括止推环和止推垫圈,且其中止推坏被配置为随着紧固件被拧紧而把止推垫圈压靠轴肩。
4.如权利要求3所述的涡轮增压器,其中发动机油被引导润滑止推轴承组件,并在止推垫圈和止推墙之间产生油膜。
5.如权利要求1所述的涡轮增压器,其中止推轴承组件压在轴上在止推轴承组件和轴之间产生范围在约5-15μm之间的过盈配合。
6.如权利要求1所述的涡轮增压器,其中所述压缩机轮被压在轴上。
7.如权利要求6所述的涡轮增压器,其中将压缩机轮压在轴上在压缩机轮和轴之间产生了范围在约25-30μm之间的过盈配合。
8.如权利要求1所述的涡轮增压器,其中所述止推轴承组件沿轴线布置在轴上,位于轴颈轴承和压缩机叶轮之间。
9.一种用于内燃发动机的涡轮增压器,该涡轮增压器包括:
轴承壳体,其包括轴承孔和止推墙;
轴颈轴承,其布置在孔内;
轴,其具有第一端部和第二端部,该轴由轴颈轴承支撑,以在孔内绕轴线旋转;
涡轮叶轮,其固定至所述轴且靠近第一端部,且该涡轮叶轮配置为通过发动机排出的燃烧后气体绕所述轴线旋转;
压缩机叶轮,其被压在所述轴上且靠近第二端部,且配置为对从周围环境接收的气流加压,以输送至发动机;和
止推环和止推垫圈,其各自压在所述轴上且一起配置为传输由涡轮叶轮产生的推力至止推墙。
其中:
止推环配置为随着紧固件被拧紧而把止推垫圈压靠轴肩;和
被压在轴上的压缩机轮、止推环、和止推垫圈使得止推环、止推垫圈和轴之间的径向运动最小化。
10.如权利要求9所述的涡轮增压器,其中:
所述轴包括轴肩,所述压缩机叶轮经由紧固件保持在轴上,且其中随着紧固件被拧紧,压缩机叶轮被压靠止推轴承组件且止推轴承组件被压靠轴肩;
止推环和止推垫圈压在轴上在止推环、止推垫圈和轴之间产生了范围在约5-15μm之间的过盈配合;且
压缩机叶轮压在轴上在压缩机叶轮和轴之间产生范围在约25-30μm之间的过盈配合。
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Also Published As
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US8991175B2 (en) | 2015-03-31 |
CN103362641B (zh) | 2016-08-03 |
DE102013205020A1 (de) | 2013-10-02 |
US20130255252A1 (en) | 2013-10-03 |
DE102013205020B4 (de) | 2016-05-12 |
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