CN218266870U - 滑动式等速万向联轴器 - Google Patents
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- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
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- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D3/224—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
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- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
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- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D3/224—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
- F16D3/2245—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere where the groove centres are offset from the joint centre
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- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D3/226—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a cylinder co-axial with the respective coupling part
- F16D3/227—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a cylinder co-axial with the respective coupling part the joints being telescopic
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- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
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- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
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Abstract
具备降低滑动阻力、即使高常用工作角也能确保耐久性、满足稳定的等速性的DOJ新规格的滑动式等速万向联轴器。其包括形成有直线状的多个滚道槽(7)的外侧联轴器构件(2)、形成有直线状的多个滚道槽(9)的内侧联轴器构件(3)、多个转矩传递滚珠(4)以及将转矩传递滚珠收容于凹袋(5a)的保持架(5),保持架的球状外周面(11)的曲率中心(O1)与球状内周面(12)的曲率中心(O2)相对于联轴器中心(O)向轴向的相反侧偏置,其中,在内侧联轴器构件的球状外周面(Rc2)与保持架的球状内周面(12)之间形成有能进行接触引导的球面间隙(δ3),且在保持架的凹袋(5a)与转矩传递滚珠(4)之间形成有正的轴向间隙。
Description
技术领域
本实用新型涉及机动车、各种工业机械等的动力传递***、例如机动车的驱动轴、传动轴所使用的滑动式等速万向联轴器。
背景技术
应用于机动车的驱动轴的等速万向联轴器大致分为仅允许2轴间的角度位移的固定式等速万向联轴器和允许角度位移及轴向位移的滑动式等速万向联轴器。机动车的驱动轴通常在驱动车轮侧(也称为外盘侧)使用固定式等速万向联轴器,在差速器侧(也称为内盘侧)使用滑动式等速万向联轴器,通过中间轴将这2个等速万向联轴器连结而构成。等速万向联轴器分别根据使用条件、用途等而进行各种选择。
作为滑动式等速万向联轴器,代表性的是双偏置型等速万向联轴器(DOJ)、三球销型等速万向联轴器(TJ)。DOJ型的滑动式等速万向联轴器由于制造成本低廉、联轴器内部的旋转方向晃动少而被广泛使用。另外,已知DOJ类型的滑动式等速万向联轴器的滚珠的个数为6个或8个,在专利文献1中记载有将滚珠个数设为8个的紧凑设计的DOJ,在专利文献2中记载有实现了工作角的高角化和更轻量、紧凑化的最大工作角为30°以上的DOJ。
近年来,随着EV(电动机动车)、SUV(运动型多用途汽车)的市场受欢迎,能够应对联轴器内部的旋转方向晃动少、高常用工作角化、最大工作角的高角化的DOJ型的应用有增加倾向。其理由是,在EV中要求转矩负载响应性,旋转方向晃动小的DOJ型是适合的。另外,在SUV中,为了提高通过性,要求通过将差速器的位置设定得较高而实现的高常用工作角化(8°以上,例如10°)、最大工作角的进一步高角化(30°以上,例如35°),DOJ型是适合的。
在滑动式等速万向联轴器中,通常在悬架最大程度地伸长的完全回弹状态时成为最大工作角。关于常用工作角,现状的乘用车等的驱动轴中的以往的常用工作角比较小,通常以6°左右使用。
在TJ类型中,若常用工作角变高,则诱发推力(3次分量)变大,成为起步时车辆横摆的原因。另一方面,DOJ型与TJ型相比,滑动阻力大,在振动方面存在缺点。
为了降低DOJ型的联轴器内部的滑动阻力,提出了在内侧联轴器构件的球状外周面与保持架的球状内周面之间设置轴向间隙,并且在滚珠与保持架的凹袋之间设置微小的凹袋间隙的技术方案(专利文献3)。
现有技术文献
专利文献
专利文献1:日本特开平10-73129号公报
专利文献2:日本特开2007-85488号公报
专利文献3:日本特开2002-54650号公报
实用新型内容
实用新型要解决的课题
在以往的机动车中,由于发动机的振动级别大,因此在不将内侧联轴器构件与保持架之间的轴向间隙设置为1mm以上时,无法吸收当时的发动机的振动以降低滑动阻力。因此,采用了专利文献3那样的方法。但是,若内侧联轴器构件与保持架之间的轴向间隙大,则也担心等速性变得不稳定。
另一方面,作为技术动向,在最近的机动车中,发动机的低振动化不断发展,在EV中,驱动源的振动被大大降低。着眼于这样的最新的技术动向,本实用新型发现了满足滑动阻力、高常用工作角时的耐久性、等速性的DOJ的新规格。关于达到本实用新型的开发过程的构思、见解,在后面叙述。
本实用新型鉴于上述问题,其目的在于提供一种具备降低滑动阻力、即使是高常用工作角也能够确保耐久性、满足稳定的等速性的DOJ的新规格的滑动式等速万向联轴器。
用于解决课题的方案
本实用新型的发明人等为了实现上述目的而进行了各种研究、验证的结果想到了如下的DOJ的新规格,即、以将保持架的球状内周面的曲率半径与内侧联轴器构件的球状外周面的曲率半径设为大致相同且在保持架的球状内周面与内侧联轴器构件的球状外周面之间形成有能够进行接触引导的球面间隙的标准型的球面规格为基础,在保持架的凹袋与转矩传递滚珠之间形成正的轴向间隙,从而完成了本实用新型。
作为实现上述目的的技术方案,本实用新型的滑动式等速万向联轴器包括:外侧联轴器构件,其在圆筒状内周面沿着轴向形成有直线状的多个滚道槽;内侧联轴器构件,其在球状外周面沿着轴向形成有与所述外侧联轴器构件的直线状的多个滚道槽对置的直线状的多个滚道槽;多个转矩传递滚珠,其组装于所述外侧联轴器构件的直线状的多个滚道槽与所述内侧联轴器构件的直线状的多个滚道槽之间;以及保持架,其将所述转矩传递滚珠收容于凹袋,并具有被所述外侧联轴器构件的圆筒状内周面和所述内侧联轴器构件的球状外周面接触引导的球状外周面和球状内周面,所述保持架的球状外周面的曲率中心和球状内周面的曲率中心相对于联轴器中心向轴向的相反侧偏置,其特征在于,在所述内侧联轴器构件的球状外周面与所述保持架的球状内周面之间形成有能够进行接触引导的球面间隙,并且在所述保持架的凹袋与所述转矩传递滚珠之间形成有正的轴向间隙。根据上述的结构,能够实现具备降低滑动阻力、即使是高常用工作角也能够确保耐久性、满足稳定的等速性的DOJ的新规格的滑动式等速万向联轴器。
具体而言,通过在上述的保持架的凹袋与转矩传递滚珠之间将正的轴向间隙设为+0.001mm~+0.050mm,从而在转矩传递滚珠的外侧联轴器构件、内侧联轴器构件的滚道槽上滚动区域增大,实现滑动阻力的降低。
通过将上述的滑动式等速万向联轴器的内部的旋转方向晃动量设为15分以下,从而EV车的转矩负载响应性也良好。
优选将上述的外侧联轴器构件的滚道槽和内侧联轴器构件的滚道槽各自的横截面形状设为与转矩传递滚珠进行角接触的哥特式拱形状。由此,能够可靠地抑制联轴器内部的旋转方向晃动。
通过将上述的多个转矩传递滚珠的个数设为5~8个,能够构成适合于机动车、各种工业机械等的动力传递***的滑动式等速万向联轴器。
实用新型效果
根据本实用新型的滑动式等速万向联轴器,能够实现具备降低滑动阻力、即使是高常用工作角也能够确保耐久性、满足稳定的等速性的DOJ的新规格的滑动式等速万向联轴器。
附图说明
图1是本实用新型的一实施方式的滑动式等速万向联轴器的纵剖视图,并且是图2的B-N-B线处的纵剖视图。
图2是本实用新型的一实施方式的滑动式等速万向联轴器的横剖视图,并且是图1的A-A线的横剖视图。
图3是表示本实施方式的滑动式等速万向联轴器的滚道槽与转矩传递滚珠的角接触以及内部的旋转方向晃动的横剖视图。
图4是表示转矩传递滚珠与保持架的凹袋之间的轴向间隙的纵剖视图。
图5是表示本实施方式的滑动式等速万向联轴器的转矩传递滚珠与保持架的凹袋之间的轴向间隙及内侧联轴器构件的球状外周面与保持架的球状内周面之间的球面间隙的纵剖视图。
图6是对比了较高的常用工作角的状态与以往的常用工作角的状态的示意图。
图7是表示本实施方式的滑动式等速万向联轴器与以往的标准规格品的滑动阻力的试验结果的图表。
图8是表示本实施方式的滑动式等速万向联轴器与以往的标准规格品的外侧联轴器构件的表面温度上升量的试验结果的图表。
附图标记说明
1 滑动式等速万向联轴器
2 外侧联轴器构件
3 内侧联轴器构件
4 转矩传递滚珠
5 保持架
5a 凹袋
6 圆筒状内周面
7 滚道槽
8 球状外周面
9 滚道槽
11 球状外周面
12 球状内周面
DBALL 滚珠直径
F 偏置量
O 联轴器中心
O1 曲率中心
O2 曲率中心
δ1 圆周方向的滚道间隙
δ2 滚珠与凹袋之间的正的轴向间隙
δ3 球面间隙
δ4 保持架与内侧联轴器构件之间的轴向间隙。
具体实施方式
基于图1~图8对本实用新型的一实施方式的滑动式等速万向联轴器进行说明。图1是本实施方式的滑动式等速万向联轴器的纵剖视图,并且是图2的B-N-B线处的纵剖视图。图2是本实施方式的滑动式等速万向联轴器的横剖视图,并且是图1的A-A线处的横剖视图。图3是表示本实施方式的滑动式等速万向联轴器的滚道槽与转矩传递滚珠的角接触以及内部的旋转方向晃动的横剖视图。图4是表示转矩传递滚珠与保持架的凹袋之间的轴向间隙的纵剖视图,图5是表示本实施方式的滑动式等速万向联轴器的转矩传递滚珠与保持架的凹袋之间的轴向间隙及内侧联轴器构件的球状外周面与保持架的球状内周面之间的球面间隙的纵剖视图。图6是对比了较高的常用工作角的状态与以往的常用工作角的状态的示意图。图7是表示本实施方式的滑动式等速万向联轴器与以往的标准规格品的滑动阻力的试验结果的图表,图8是表示本实施方式的滑动式等速万向联轴器与以往的标准规格品的外侧联轴器构件的表面温度上升量的试验结果的图表。
如图1、图2所示,滑动式等速万向联轴器1是所谓的双偏置型滑动式等速万向联轴器(有时也简称为DOJ),以外侧联轴器构件2、内侧联轴器构件3、转矩传递滚珠4以及保持架5为主要结构。在外侧联轴器构件2的圆筒状内周面6上,8条滚道槽7在圆周方向上等间隔且沿轴向形成为直线状。在内侧联轴器构件3的球状外周面8,与外侧联轴器构件2的滚道槽7对置的滚道槽9沿圆周方向等间隔且沿轴向形成为直线状。在外侧联轴器构件2的滚道槽7与内侧联轴器构件3的滚道槽9之间一个一个地组装有8个转矩传递滚珠(以下,也简称为滚珠)4。滚珠4收容于保持架5的凹袋5a。
保持架5具有球状外周面11和球状内周面12,球状外周面11与外侧联轴器构件2的圆筒状内周面6嵌合而被接触引导,球状内周面12与内侧联轴器构件3的球状外周面8嵌合而被接触引导。保持架5的球状外周面11以作为曲率中心O1的曲率半径Rc1形成,球状内周面12以作为曲率中心O2的曲率半径Rc2形成。内侧联轴器构件3的球状外周面8以作为曲率中心O2的曲率半径Ri形成。曲率中心O1、O2位于轴线N上,相对于联轴器中心O在轴向上以等距离F偏置。由此,在联轴器具有工作角的情况下,滚珠4始终被引导至将外侧联轴器构件2与内侧联轴器构件3的两轴线所成的角度二等分的平面上,在两轴间以等速旋转的方式传递。
在外侧联轴器构件2的开口侧端部设置挡圈槽15,在该挡圈槽15安装挡圈17,防止图1所示的内侧联轴器构件3、滚珠4、保持架5的内侧组装体从外侧联轴器构件2的开口侧端部脱落。在外侧联轴器构件2的开口侧端部的外周设置有保护罩装配槽16。在外侧联轴器构件2的开口相反侧一体地形成有杆部(轴部)2b,并与差速器(省略图示)连结。
由于在内侧联轴器构件3的球状外周面8形成有直线状的滚道槽9,因此,滚道槽9的槽深度随着从内侧联轴器构件3的轴向的中心趋向两端而变浅。在内侧联轴器构件3的连结孔13形成有花键(包括锯齿,以下相同)14,中间轴(省略图示)的轴端部花键嵌合,通过中间轴肩部和挡圈沿轴向固定于内侧联轴器构件3。
在图1的A-A线所示的保持架5的轴向中心沿圆周方向等间隔地设置有8个凹袋5a,相邻的凹袋5a之间成为柱部5b(参照图2)。在保持架5的大径侧端部的内周设置有用于组装内侧联轴器构件3的切口5c。保持架5的限位面5d形成为与球状外周面11作为切线连接的圆锥状。在本实施方式的滑动式等速万向联轴器1中,最大工作角例如设定为25°。保持架5在联轴器具有工作角的情况下,仅倾斜外侧联轴器构件2与内侧联轴器构件3的两轴线所成的角度的一半,因此限位面5d的倾斜角度S设定为12.5°。由此,能够限制滑动式等速万向联轴器1的最大允许角度。
基于图3,对外侧联轴器构件2的滚道槽7、内侧联轴器构件3的滚道槽9与转矩传递滚珠4的角接触以及内部的旋转方向晃动进行说明。图3表示图2的B-N线处的1个滚道槽7、9、转矩传递滚珠4。外侧联轴器构件2的滚道槽7与内侧联轴器构件3的滚道槽9的横截面形成为将2个圆弧组合而成的哥特式拱形状。因此,滚珠4相对于滚道槽7、9在各2个点C1、C2、C3、C4进行角接触。滚道槽7、9的横截面形状不限于上述的哥特式拱形状,也可以是椭圆形状。
如图3所示,将外侧联轴器构件2的滚道槽7的节圆直径设为ToPCD,将内侧联轴器构件3的滚道槽9的节圆直径设为TiPCD。ToPCD设定为比TiPCD的中央值大例如0.050mm左右。其结果是,转矩传递滚珠4的中心Ob位于ToPCD与TiPCD之间的径向中间,在滚珠4与外侧联轴器构件2的滚道槽7及内侧联轴器构件3的滚道槽9之间在滚道接触角α方向上形成有滚道间隙。基于滚道接触角α方向的滚道间隙,产生圆周方向的滚道间隙δ1。而且,使内侧联轴器构件3与外侧联轴器构件2相对旋转时的联轴器内部的旋转方向晃动量为圆周方向的滚道间隙δ1的4倍。
在本实施方式的滑动式等速万向联轴器1中,将联轴器内部的旋转方向晃动量设定为15分以下,因此,EV中的转矩负载响应性也良好。另外,滚道槽7、9的横截面形状形成为哥特式拱形状,因此能够可靠地抑制联轴器内部的旋转方向晃动量。在图3中,夸张地图示了TiPCD与ToPCD的尺寸差、滚道间隙。
滚道接触角α是图3的直线La与直线Lb之间的角度α。直线La是滚道槽7、9的横截面的中心线,与图2的B-N线对应。直线Lb是将滚道槽7、9的侧面的滚珠4的接触点C1、C2、C3、C4与滚珠4的中心Ob连结的直线。
接着,基于图4对保持架5的凹袋5a与转矩传递滚珠4之间的轴向间隙进行说明。若将滚珠4的直径设为DBALL,将保持架5的凹袋5a的宽度设为Lw,则在Lw<DBALL的情况下成为负的轴向间隙,滚珠4与凹袋5a之间成为过盈量。另一方面,在Lw>DBALL的情况下成为正的轴向间隙,滚珠4与凹袋5a之间成为间隙。
在此,对完成本实用新型的开发过程的构思、见解进行说明。本实用新型的发明人发现,作为技术动向,在最近的机动车中,发动机的低振动化不断发展,在EV中,驱动源的振动极其降低。着眼于这样的最新的技术动向,对以往的标准规格的DOJ的球面间隙进行了研究。该研究成为引导至本实用新型的线索。
到标准规格的DOJ的球面间隙为止,能够进行保持架5的球状内周面12与内侧联轴器构件3的球状外周面8之间的接触引导的球面间隙的中央值为0.050mm左右。通过该球面间隙,保持架5与内侧联轴器构件3之间的轴向间隙量为0.15mm左右。因此,内侧联轴器构件3相对于外侧联轴器构件2的轴向的可移动量为0.15mm左右的2倍即0.30mm。
如上所述,若以作为最新的技术动向的发动机的低振动化、驱动源的低振动化为契机,想到了以标准规格的DOJ的球面间隙为基础,打开滚珠4与保持架5的凹袋5a间的轴向间隙,则内侧联轴器构件3相对于外侧联轴器构件2在0.30mm的范围内通过滚珠的顺畅的滚动而能够实现较小的滑动阻力的构思。基于上述内容,发现了满足滑动阻力、高常用工作角时的耐久性、等速性的DOJ的新规格。而且,在最近的发动机车中,低振动化不断发展,验证了能够以上述范围的轴向晃动量充分地吸收振动。
上述那样的关注、研究、构思、验证对于本领域技术人员而言是首次的尝试。其原因在于,以往的发动机振动较大的时代的保持架与内侧联轴器构件之间的轴向间隙量设置为1mm以上,若不设置该程度的轴向间隙量,则无法利用联轴器吸收发动机的振动,这对于本领域技术人员而言多年未变。
本实施方式的滑动式等速万向联轴器1的特征结构实现了具备如下DOJ的新规格的滑动式等速万向联轴器,即、(1)将保持架的球状内周面的曲率半径与内侧联轴器构件的球状外周面的曲率半径设为大致相同,在保持架的球状内周面与内侧联轴器构件的球状外周面之间形成有能够进行接触引导的球面间隙的标准型的球面规格作为基础、(2)在保持架的凹袋与转矩传递滚珠之间形成正的轴向间隙。
基于图5对本实施方式的滑动式等速万向联轴器1的特征性结构进行具体说明。图5放大图1的主要部分,夸张地图示转矩传递滚珠4与保持架5的凹袋5a之间的轴向间隙以及内侧联轴器构件3的球状外周面8与保持架5的球状内周面12之间的球面间隙。在滚珠4与保持架5的凹袋5a之间形成有正的轴向间隙δ2。正的轴向间隙δ2=Lw-DBALL,δ2优选为+0.001mm~+0.050mm。由此,滚珠4能够在凹袋5a内顺畅地滚动,在滚珠4的外侧联轴器构件2、内侧联轴器构件3的滚道槽7、9上滚动区域增大,实现滑动阻力降低。在本实施方式的滑动式等速万向联轴器1中,设定为δ2=+0.001mm~+0.050mm。
保持架5的球状内周面12以作为曲率中心O2的曲率半径Rc2形成,内侧联轴器构件3的球状外周面8以作为曲率中心O2的曲率半径Ri形成。保持架5的球状内周面12与内侧联轴器构件3的球状外周面8之间的球面间隙δ3=2×(Rc2-Ri),球面间隙δ3的中央值为0.050mm左右。球面间隙δ3是指能够进行本说明书及技术方案中的内侧联轴器构件的球状外周面与保持架的球状内周面之间的接触引导的球面间隙。
基于球面间隙δ3的保持架5与内侧联轴器构件3之间的单侧的轴向间隙δ4/2为0.15mm左右,内侧联轴器构件3相对于外侧联轴器构件2的轴向的可移动量为0.15mm左右的2倍即0.30mm。在正在推进低振动化的最近的发动机车中,能够以上述范围的轴向的可移动量充分地吸收振动。因此,保持架5与内侧联轴器构件3之间的轴向间隙δ4和滚珠4与保持架5的凹袋5a之间的正的轴向间隙δ2相互作用,能够降低滑动阻力。另外,能够满足高常用工作角时的耐久性、等速性。
图6是将近年来的SUV中的较高的常用工作角(例如,10°左右)的状态与以往的常用工作角的状态进行对比的示意图。如图6所示,驱动轴20的外侧端的固定式等速万向联轴器21与车轮W连结,内侧端的滑动式等速万向联轴器1与差速器Df连结。图6的左半部分表示较高的常用工作角θ1的状态,右半部分表示以往的常用工作角θ2的状态。在高的常用工作角θ1的情况下,差速器Df距地面的高度比以往的常用工作角θ2的情况高Δh,通过性提高。但是,由于常用工作角变高,因此施加于转矩传递滚珠的载荷增大。
在此,对本说明书中的常用工作角进行定义。常用工作角是指在水平且平坦的路面上1人乘坐时的机动车中,在使方向盘成为直行状态时由驱动轴的滑动式等速万向联轴器产生的工作角。目前的乘用车等的驱动轴中的以往的常用工作角比较小,通常以6°左右使用。
使用工作角越高,则DOJ型的滑动式等速万向联轴器的耐久性越降低。在DOJ型的滑动式等速万向联轴器中,若带有工作角,则在旋转1圈中作用于滚珠的力变动,在最大负载时,从工作角0°时的百分之几起根据角度而负载数倍的载荷。例如,若常用工作角变高,常用工作角从现状的常用工作角的6°向10°高角化,则施加于滚珠的最大载荷变高20~30%左右。
[实施例1]
在使保持架5的球状内周面12与内侧联轴器构件3的球状外周面8之间的球面间隙δ3以中央值计为0.050mm左右的标准类型的球面规格下,对于在保持架5的凹袋5a与转矩传递滚珠4之间形成正的轴向间隙的结构(凹袋间隙品)和负的轴向间隙(凹袋过盈品),对滑动阻力及外侧联轴器构件(外圈)的表面温度上升量进行试验评价。试验品是使用了8个滚珠的NTN名称EDJ,联轴器尺寸是#104。
对DOJ型的滑动式等速万向联轴器1的滑动阻力进行解析,发现了作为对降低滑动阻力有效的对策,保持架5的凹袋5a与滚珠4之间的正的轴向间隙δ2做出了贡献。验证了通过赋予该正的轴向间隙δ2,在滚珠4与外侧联轴器构件2、内侧联轴器构件3的滚道7、9槽上滚动区域增大,由此实现滑动阻力的降低。滑动阻力的试验结果如图7所示。
<试验条件>
·负载转矩:98Nm
·无旋转
·轴向加振幅:±0.1mm(频率20Hz)
使用工作角越高,则DOJ型的滑动式等速万向联轴器1的耐久性越降低。若工作角变高,则施加于滚珠4的载荷增大,从而滚道表面压力增加。由此,联轴器旋转中的发热也变大,导致耐久性的降低。作为其对策,验证了在保持架5的凹袋5a与滚珠4之间赋予正的轴向间隙δ2对于抑制发热是有效的,通过抑制滚珠4与外侧联轴器构件2、内侧联轴器构件3的滚道槽7、9间的滑动而进行滚动,能够减少滚珠4与滚道槽7、9间的摩擦。外圈温度上升量的试验结果如图8所示。特别是在高常用工作角时(10°)效果显著。
<试验条件>
·负载转矩:373Nm
·转速:200rpm
·工作角:5°、10°
在上述的实施方式、实施例中,例示了使用8个转矩传递滚珠4的DOJ型的滑动式等速万向联轴器1,但并不局限于此,能够在5~8个的范围内适当地实施转矩传递滚珠4的个数。能够构成适合于机动车、各种工业机械等的动力传递***的滑动式等速万向联轴器。另外,也可以将转矩传递滚珠4的个数设为8个以上。
本实用新型不受上述的实施方式、实施例的任何限定,在不脱离本实用新型的主旨的范围内,当然能够进一步以各种方式实施,本实用新型的范围由技术方案示出,还包括与技术方案记载的等同的含义和范围内的全部变更。
Claims (5)
1.一种滑动式等速万向联轴器,其包括:外侧联轴器构件,其在圆筒状内周面沿着轴向形成有直线状的多个滚道槽;内侧联轴器构件,其在球状外周面沿着轴向形成有与所述外侧联轴器构件的直线状的多个滚道槽对置的直线状的多个滚道槽;多个转矩传递滚珠,其组装于所述外侧联轴器构件的直线状的多个滚道槽与所述内侧联轴器构件的直线状的多个滚道槽之间;以及保持架,其将所述转矩传递滚珠收容于凹袋,并具有被所述外侧联轴器构件的圆筒状内周面和所述内侧联轴器构件的球状外周面接触引导的球状外周面和球状内周面,所述保持架的球状外周面的曲率中心和球状内周面的曲率中心相对于联轴器中心向轴向的相反侧偏置,其特征在于,
在所述内侧联轴器构件的球状外周面与所述保持架的球状内周面之间形成有能够进行接触引导的球面间隙,并且,
在所述保持架的凹袋与所述转矩传递滚珠之间形成有正的轴向间隙。
2.根据权利要求1所述的滑动式等速万向联轴器,其特征在于,
在所述保持架的凹袋与所述转矩传递滚珠之间,正的轴向间隙为+0.001mm~+0.050mm。
3.根据权利要求1或2所述的滑动式等速万向联轴器,其特征在于,
所述滑动式等速万向联轴器的内部的旋转方向晃动量为15分以下。
4.根据权利要求1或2所述的滑动式等速万向联轴器,其特征在于,
将所述外侧联轴器构件的滚道槽和所述内侧联轴器构件的滚道槽各自的横截面形状设为与所述转矩传递滚珠进行角接触的哥特式拱形状。
5.根据权利要求1或2所述的滑动式等速万向联轴器,其特征在于,
所述多个转矩传递滚珠的个数为5~8个。
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