WO2015000318A1 - 防松动螺纹件 - Google Patents

防松动螺纹件 Download PDF

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Publication number
WO2015000318A1
WO2015000318A1 PCT/CN2014/075346 CN2014075346W WO2015000318A1 WO 2015000318 A1 WO2015000318 A1 WO 2015000318A1 CN 2014075346 W CN2014075346 W CN 2014075346W WO 2015000318 A1 WO2015000318 A1 WO 2015000318A1
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WO
WIPO (PCT)
Prior art keywords
thread
external thread
internal
internal thread
wedge
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Application number
PCT/CN2014/075346
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English (en)
French (fr)
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WO2015000318A9 (zh
WO2015000318A8 (zh
Inventor
许松林
Original Assignee
Xu Songlin
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Priority claimed from CN2013203914176U external-priority patent/CN203335597U/zh
Priority claimed from CN201310275676.7A external-priority patent/CN103291729B/zh
Application filed by Xu Songlin filed Critical Xu Songlin
Priority to US14/898,842 priority Critical patent/US20160153486A1/en
Priority to CA2915891A priority patent/CA2915891C/en
Priority to EP14820287.2A priority patent/EP3018367A4/en
Priority to KR1020157035814A priority patent/KR20160003315A/ko
Priority to JP2016520250A priority patent/JP2016524681A/ja
Publication of WO2015000318A1 publication Critical patent/WO2015000318A1/zh
Publication of WO2015000318A8 publication Critical patent/WO2015000318A8/zh
Publication of WO2015000318A9 publication Critical patent/WO2015000318A9/zh

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Classifications

    • 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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B39/00—Locking of screws, bolts or nuts
    • F16B39/22—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening
    • F16B39/28—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening by special members on, or shape of, the nut or bolt
    • F16B39/30—Locking exclusively by special shape of the screw-thread

Definitions

  • the present invention relates to a anti-loose screw member.
  • the coefficient of friction between the flank and the angle of the thread reaches a certain value, so that the longitudinal self-locking of the coupling pair of the threaded member can be achieved.
  • One end of the nut is in contact with the bolt head and has a certain
  • the pre-tightening screw coupling pair is taken as an example: the bolt head is oriented upwards perpendicular to the horizontal plane, and the screw coupling pair makes the movement of the hard fixture at a certain speed in the forward horizontal straight direction (only the bolt head and the impact moment) Fixation contact).
  • the bolt and the nut are divided into left and right sides by a plane containing the longitudinal central axis of the mutually overlapping internal threads and the longitudinal central axis of the external thread and the direction of movement of the coupling member of the threaded member, the left external thread of the bolt
  • the upper flank is a downward curved bevel
  • the upper flank of the right external thread of the bolt is an upward curved bevel.
  • the contact surface of the upper flank of the external thread is a fulcrum (in theory, the upper and lower flank of the common cylindrical thread and the upper and lower flank of the external thread are arranged by a plurality of mutually non-parallel straight lines along the spiral of the thread, Therefore, between the lower flank of one internal thread of a common cylindrical thread that is in contact with each other and the upper flank of one external thread, the upper flank of the internal thread and the upper flank of the external thread are only changed. Between, there will be only one contact point instead of the contact surface, so this contact point is the theoretical fulcrum.) The tendency to make a leftward rotational motion, so when the threaded member joins the secondary impact on the fixture, the resultant force of the nut exceeds a certain value.
  • the nut will be moved without a fixed axial left rotation, that is, the movement of the nut relative to the bolt, and the lateral clearance between the inner and outer threads just provides the space for the nut to perform a fixed axial left rotation.
  • a small experiment below Put a circle on a horizontally suspended cylindrical pencil with an inner diameter that is more than twice the outer diameter of the pencil (so that it is easy to experiment and also magnify the visual effect of the experiment).
  • the circle will make a longitudinal rotation without a fixed axis, and as long as the thrust direction is constant, the direction of rotation of the circle does not change.
  • the direction of rotation of the circle also changes.
  • the common cylindrical screw coupling pair is in the environment of lateral vibration or impact, because the spiral structure of the thread, one side inside and outside The friction between the flank of the thread is greater than the friction between the flank of the inner and outer threads of the other side, so the internally threaded or externally threaded member will produce a larger frictional inner and outer thread.
  • the contact surface of the flank is a tendency for the fulcrum to perform a lateral rotation motion.
  • the internally threaded member or the externally threaded member will perform a lateral rotation without a fixed axis.
  • the direction of lateral rotation is the direction in which the inner and outer threaded members are relatively retracted, and the lateral gap between the inner and outer threads provides space for the lateral rotation of the inner and outer threaded members without a fixed axis, and
  • the dynamic friction factor between the flank of the external thread and the inclination of the flank cannot satisfy the condition of the lateral self-locking of the coupling pair of the screw.
  • the internal or external thread of the Spiralock cylindrical screw has a wedge-shaped bevel at an angle of 30° to the longitudinal central axis of the internal or external thread, and most of the cylindrical threaded parts that need to be loosened are coupled to the threaded surface of the pair.
  • the dynamic friction factor is less than tan30° (0.577), so the surface of the internal or external thread cannot be laterally locked with the wedge bevel. Therefore, the recommended large preload should be used to make the surface of the internal or external thread.
  • the structure is deformed to form a lateral locking relationship with the wedge-shaped inclined surface, thereby effectively preventing the lateral rotation of the fixed shaft between the inner and outer threaded members, so that the effective locking of the cylindrical threaded coupling pair can be achieved.
  • the object is stationary on the inclined surface.
  • the inclined angle of the inclined surface is called the friction angle.
  • the dynamic friction factor between the inner and outer threads should not be greater than 0.15.
  • the present invention provides a anti-loose screw member, as long as the pre-tightening force enables the surface of the internal or external thread and the wedge-shaped inclined surface to be in close contact with each other. , it can realize the effective anti-loose of the cylindrical screw coupling pair of various material thread surfaces.
  • the technical solution adopted by the present invention is: a cylindrical internal thread is arranged in the inner hole of the internal threaded member, and a cylindrical external thread is arranged on the screw of the externally threaded member, and the surface of the internal thread and the external thread is not Covered with a loose material, the internal or external thread has a wedge-shaped bevel at an angle ⁇ or angle ⁇ to the longitudinal central axis of the internal or external thread, tan ot or tan ⁇ is smaller than the wedge-shaped bevel and internal or external
  • the structure can effectively prevent the lateral rotation of the fixed shaft between the inner and outer threaded members, that is, the effective anti-loose between the cylindrical inner screw member and the cylindrical outer screw member.
  • the dynamic friction factor between the inner and outer threads of the inner and outer threaded parts should not be greater than 0.15 and that tan a or tan ⁇ cannot become zero (because of internal threads) 5 ⁇
  • the longitudinal axis of the external thread is not possible on the wedge-shaped slope), so it is preferable that tan a or tan ⁇ is greater than 0 is less than 0.15.
  • the utility model has the beneficial effects that: the above-mentioned anti-loose screw member can realize the cylindrical screw coupling pair of various material thread surfaces as long as the pre-tightening force can make the surface of the internal thread or the external thread and the wedge-shaped inclined surface are in close contact with each other. Effective anti-loose.
  • the above-mentioned anti-loose screw member has a simple structure and is convenient to use, and can realize mass production by using existing processes and equipment.
  • FIG. 1 is a schematic side elevational view, partly in section, of a coupling member of a screw member after screwing and screwing between an internally threaded member and an externally threaded member according to a first embodiment of the present invention
  • Figure 2 is a partial enlarged view of Figure 1;
  • Figure 3 is a central longitudinal sectional side elevational view of the coupling member of the screw member after the internal screw member and the male screw member of the second embodiment of the present invention are screwed together;
  • Figure 4 is a partial enlarged view of Figure 3;
  • the anti-loose threaded member comprises an internally threaded member 1 and an externally threaded member 2, wherein: as shown in Fig. 1, the inner threaded member 1 is provided with a cylindrical internal thread 3 and an external thread.
  • the screw of the piece 2 is provided with a cylindrical external thread 4; the surface of the internal thread 3 and the external thread 4 is not covered with a loosening material; as shown in FIG. 2, the root of the external thread 4 has a longitudinal central axis with the external thread 4.
  • 5 is a wedge-shaped inclined surface 6 with an angle ⁇ ; tan a is smaller than the dynamic friction coefficient between the contact surface of the wedge-shaped inclined surface 6 and the internal thread 3; as shown in Fig.
  • the internal threaded member 1 and the externally threaded member 2 are mutually rotated After the tightening, the surface of the internal thread 3 and the wedge-shaped inclined surface 6 are in close contact with each other.
  • the tan a is greater than 0 and less than 0.15.
  • the anti-loose screw member includes an internally threaded member 1 and an externally threaded member 2, wherein: as shown in FIG. 3, the inner threaded member 1 is provided with a cylindrical internal thread 3 and an external thread.
  • the screw of the piece 2 is provided with a cylindrical external thread 4; the surfaces of the internal thread 3 and the external thread 4 are not covered with a loosening material; as shown in FIG. 4, the root of the internal thread 3 has a longitudinal central axis with the internal thread 3 5 is a wedge-shaped inclined surface 6 with an angle ⁇ ; tan P is smaller than the dynamic friction coefficient between the contact surface of the wedge-shaped inclined surface 6 and the external thread 4; as shown in Figs.
  • the internally threaded member 1 and the externally threaded member 2 are mutually rotated. After tightening, the surface of the external thread 4 and the wedge-shaped bevel 6 are in close contact with each other.
  • the tan ⁇ is greater than 0 and less than 0.15.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bolts, Nuts, And Washers (AREA)
  • Mutual Connection Of Rods And Tubes (AREA)
  • Dowels (AREA)

Abstract

一种防松动螺纹件，包括内螺纹件（1）与外螺纹件（2）。内螺纹件（1）的内孔中设置有圆柱内螺纹（3），外螺纹件（2）的螺杆上设置有圆柱外螺纹（4），外螺纹（4）或内螺纹（3）的牙底有与外螺纹（4）或内螺纹（3）的纵向中轴线（5）呈夹角α或夹角β的楔形斜面（6），tanα＜1或tanβ小于楔形斜面（6）与内螺纹（3）或外螺纹（4）的接触面之间的动摩擦因数，内、外螺纹件之间相互旋合拧紧后，内螺纹（3）或外螺纹（4）的表面与楔形斜面（6）之间是相互紧密接触的结构，也就是横向锁止的结构，只要预紧力能够使内螺纹或外螺纹的表面与楔形斜面之间相互紧密接触，就能够实现各种材质螺纹表面的圆柱螺纹件联接副的有效防松。

Description

说 明 书
防松动螺紋件 技术领域
本发明涉及到一种防松动螺纹件。
背景技术
在横向振动或冲击的环境里圆柱螺纹件联接副的松动是长期以来困扰我们 的问题， 那么在横向振动或冲击的环境里圆柱螺纹件联接副松动的原因是什么 呢？ 下面本发明人来具体分析一下：
在一组圆柱螺纹件联接副的内、 外螺纹之间， 牙侧之间的摩擦系数和螺纹 升角达到一定值， 就可以实现螺纹件联接副的纵向自锁。
普通的圆柱螺纹件联接副在拧紧的状态下不受外力的作用时， 内、 外螺纹 之间纵向、 横向都存在一定的间隙。
以一组标准右旋圆柱螺纹螺母拧紧在相应的标准右旋全牙圆柱螺纹螺栓上 (内、 外螺纹之间纵向、 横向都存在一定的间隙） ， 螺母的一端与螺栓头接触 并有一定的预紧力的螺纹件联接副为例： 螺栓头朝上垂直于水平面的姿态下， 螺纹件联接副做向前水平直线方向以一定的速度撞击坚硬的固定物的运动 （撞 击瞬间只有螺栓头与固定物接触） 。 如果以包含相互重叠的内螺纹的纵向中轴 线与外螺纹的纵向中轴线并与螺纹件联接副的运动方向相互平行的平面将螺栓 和螺母分为左右两侧， 则螺栓的左侧外螺纹的上牙侧是呈向下的弯曲斜面， 而 螺栓的右侧外螺纹的上牙侧则是呈向上的弯曲斜面， 因为这种结构， 当螺纹件 联接副撞击固定物的瞬间， 螺母的右侧内螺纹的下牙侧与螺栓的右侧外螺纹的 上牙侧之间是相互挤压的趋势， 而螺母的左侧内螺纹的下牙侧与螺栓的左侧外 螺纹的上牙侧之间是相互脱离的趋势， 所以当螺纹件联接副撞击固定物的瞬间， 螺母的右侧内螺纹的下牙侧与螺栓的右侧外螺纹的上牙侧之间的摩擦力比螺母 的左侧内螺纹的下牙侧与螺栓的左侧外螺纹的上牙侧之间的摩擦力更大， 所以 当螺纹件联接副撞击固定物的瞬间， 螺母会产生以右侧内螺纹的下牙侧与右侧 外螺纹的上牙侧的接触面为支点 （理论上， 普通圆柱螺纹的一圈内、 外螺纹的 上、 下牙侧都是由很多相互不平行的直线沿螺纹的螺旋线排列而成的， 所以相 互吻合接触的普通圆柱螺纹的一圈内螺纹的下牙侧与一圈外螺纹的上牙侧之间 只要改变相互吻合接触的状态， 在内螺纹的下牙侧与外螺纹的上牙侧之间， 就 会只有一个接触点而不是接触面， 所以这个接触点就是理论上的支点） 做向左 旋转运动的趋势， 所以当螺纹件联接副撞击固定物的瞬间螺母受到的合力超过 一定值， 螺母就会做无固定轴向左旋转的运动， 也就是螺母相对于螺栓松退的 运动， 而内、 外螺纹之间的横向间隙正好提供了螺母做无固定轴向左旋转运动 的空间。 如同下面一个小实验： 在一个水平悬置的圆柱形铅笔上套上一个内径 是铅笔的外径的两倍以上（这样便于进行实验，同时也能放大实验的视觉效果） 的圆圈， 用力推圆圈的中部， 圆圈就会做无固定轴纵向旋转的运动， 而且只要 推力方向不变， 圆圈的旋转方向也不变， 只要推力方向一变， 圆圈的旋转方向 也变。
因此， 可以认为普通圆柱螺纹件联接副在横向振动或冲击的环境里产生松 动的原因是： 普通圆柱螺纹件联接副在横向振动或冲击的环境里， 因为螺纹的 螺旋结构， 一侧内、 外螺纹的牙侧之间的摩擦力比另一侧内、 外螺纹的牙侧之 间的摩擦力更大， 所以内螺纹件或外螺纹件会产生以摩擦力更大的一侧内、 外 螺纹的牙侧的接触面为支点做横向旋转运动的趋势， 所以当内螺纹件或外螺纹 件受到的合力超过一定值时， 内螺纹件或外螺纹件就会做无固定轴横向旋转的 运动， 横向旋转的方向就是内、 外螺纹件之间相对松退的方向， 而内、 外螺纹 之间的横向间隙提供了内、 外螺纹件之间做无固定轴横向旋转运动的空间， 而 且内、 外螺纹的牙侧之间的动摩擦因数与牙侧的倾角不能满足螺纹件联接副横 向自锁的条件。
因此， 只要阻止内、 外螺纹件之间的无固定轴横向旋转运动， 就能够实现 螺纹件联接副在横向振动或冲击的环境里的完全防松。
美国的 Horace D. Holmes设计了 Spiralock螺帽， 20世纪 70年代获得了专 利并投了产， 取得了用户的极大好评， 但是 MIT (美国麻省理工学院） 的一位 教授称： "这种紧固系统的试验情况特别好，试验的目的是因为缺乏理论依据"。 通常 Spiralock圆柱螺纹件的内螺纹或外螺纹的牙底有与内螺纹或外螺纹的纵向 中轴线呈夹角 30° 的楔形斜面， 而大多数需要防松的圆柱螺纹件联接副的螺纹 表面之间的动摩擦因数都小于 tan30° ( 0.577 ) ， 所以内螺纹或外螺纹的表面 与楔形斜面之间不能横向锁止， 因此必须得用推荐的很大的预紧力使内螺纹或 外螺纹的表面与楔形斜面之间产生变形而成为横向锁止的结构， 从而有效阻止 内、 外螺纹件之间的无固定轴横向旋转运动， 才能实现圆柱螺纹件联接副的有 效防松。
物体静止在斜面上， 当斜面的倾角增大为 Θ时， 物体恰好能从斜面上匀速 下滑， 此时的斜面倾角 Θ叫做摩擦角， 根据摩擦角大小可以计算物体与斜面之 间的动摩擦因数， 即4 = 11 9， 也可以根据物体与斜面之间的动摩擦因数计算摩 擦角大小， 即 e =tan- 。 当斜面倾角小于摩擦角 Θ时， 在斜面上的物体无论变 得多重， 物体都不会滑动； 当斜面倾角大于摩擦角 Θ时， 在斜面上的物体无论 变得多重， 物体都会滑动。
螺纹紧固件的使用中， 如果内、 外螺纹之间的动摩擦因数过大， 容易导致 因夹紧力不够而使被联接件之间产生松动的危机。 根据德国汽车工业协会所制 定的 VDA 235-101 标准， 内、 外螺纹件的内、 外螺纹之间的动摩擦因数不应大 于 0. 15。
发明内容
本发明所要解决的技术问题是： 为了克服 Spiralock 圆柱螺纹件的上述不 足， 本发明提供一种防松动螺纹件， 只要预紧力能够使内螺纹或外螺纹的表面 与楔形斜面之间相互紧密接触， 就能够实现各种材质螺纹表面的圆柱螺纹件联 接副的有效防松。
为解决上述问题， 本发明采用的技术方案是： 内螺纹件的内孔中设置有圆 柱内螺纹， 外螺纹件的螺杆上设置有圆柱外螺纹， 内螺纹与外螺纹的表面上未 覆有防松材料， 内螺纹或外螺纹的牙底有与内螺纹或外螺纹的纵向中轴线呈夹 角 α或夹角 β的楔形斜面， tan ot或 tan β小于楔形斜面与内螺纹或外螺纹的接 触面之间的动摩擦因数， 内螺纹件与外螺纹件之间相互旋合拧紧后， 内螺纹或 外螺纹的表面与楔形斜面之间是相互紧密接触的结构， 也就是横向锁止的结构， 从而能有效阻止内、 外螺纹件之间的无固定轴横向旋转运动， 也就是能实现圆 柱内螺纹件与圆柱外螺纹件之间的有效防松。
根据德国汽车工业协会所制定的 VDA 235-101 标准， 内、 外螺纹件的内、 外 螺纹之间的动摩擦因数不应大于 0. 15， 而且 tan a或 tan β不可能成为 0 (因为 内螺纹或外螺纹的纵向中轴线不可能在楔形斜面上）， 所以优选 tan a或 tan β 大于 0小于 0. 15。
本发明的有益效果是： 上述的防松动螺纹件， 只要预紧力能够使内螺纹或 外螺纹的表面与楔形斜面之间相互紧密接触， 就能够实现各种材质螺纹表面的 圆柱螺纹件联接副的有效防松。上述的防松动螺纹件， 其结构简单、使用方便， 并且利用现有的工艺与设备就能实现规模生产。
附图说明
图 1 是本发明的第一实施例的内螺纹件与外螺纹件之间相互旋合拧紧后的 螺纹件联接副的中心纵剖侧视示意图；
图 2是图 1的局部放大示意图；
图 3 是本发明的第二实施例的内螺纹件与外螺纹件之间相互旋合拧紧后的 螺纹件联接副的中心纵剖侧视示意图；
图 4是图 3的局部放大示意图；
图中： 1、 内螺纹件， 2、 外螺纹件， 3、 内螺纹， 4、 外螺纹， 5、 纵向中轴 线， 6、 楔形斜面。
具体实施方式
下面通过具体实施例对本发明的防松动螺纹件作进一歩的详细描述。
实施例 1 如图 1、 图 2所示， 防松动螺纹件， 包括内螺纹件 1和外螺纹件 2， 其中： 如图 1所示， 内螺纹件 1的内孔中设置有圆柱内螺纹 3， 外螺纹件 2的螺杆上设 置有圆柱外螺纹 4;内螺纹 3与外螺纹 4的表面上未覆有防松材料；如图 2所示， 外螺纹 4的牙底有与外螺纹 4的纵向中轴线 5呈夹角 α的楔形斜面 6 ; tan a小 于楔形斜面 6与内螺纹 3的接触面之间的动摩擦因数； 如图 1、 2所示， 内螺纹 件 1与外螺纹件 2之间相互旋合拧紧后， 内螺纹 3的表面与楔形斜面 6之间是 相互紧密接触的结构。 所述的 tan a大于 0小于 0. 15。
实施例 2
如图 3、 图 4所示， 防松动螺纹件， 包括内螺纹件 1和外螺纹件 2， 其中： 如图 3所示， 内螺纹件 1的内孔中设置有圆柱内螺纹 3， 外螺纹件 2的螺杆上设 置有圆柱外螺纹 4;内螺纹 3与外螺纹 4的表面上未覆有防松材料；如图 4所示， 内螺纹 3的牙底有与内螺纹 3的纵向中轴线 5呈夹角 β的楔形斜面 6 ; tan P小 于楔形斜面 6与外螺纹 4的接触面之间的动摩擦因数； 如图 3、 4所示， 内螺纹 件 1与外螺纹件 2之间相互旋合拧紧后， 外螺纹 4的表面与楔形斜面 6之间是 相互紧密接触的结构。 所述的 tan β大于 0小于 0. 15。
上述的实施例仅例示性说明本发明创造的原理及其功效， 以及部分运用的 实施例， 而非用于限制本发明； 应当指出， 对于本领域的普通技术人员来说， 在不脱离本发明创造构思的前提下， 还可以做出若干变形和改进， 这些都属于 本发明的保护范围。

Claims

权利要求书
1、 防松动螺纹件， 包括内螺纹件与外螺纹件， 内螺纹件的内孔 中设置有圆柱内螺纹， 外螺纹件的螺杆上设置有圆柱外螺纹， 内螺纹 与外螺纹的表面上未覆有防松材料，内螺纹或外螺纹的牙底有与内螺 纹或外螺纹的纵向中轴线呈夹角 α或夹角 β的楔形斜面，内螺纹件与 外螺纹件之间相互旋合拧紧后，内螺纹或外螺纹的表面与楔形斜面之 间是相互紧密接触的结构， 其特征在于： tan a或 tan β小于楔形斜 面与内螺纹或外螺纹的接触面之间的动摩擦因数。
2、 根据权利要求 1所述的防松动螺纹件， 其特征在于： tan ot或 tan β大于 0小于 0. 15。
PCT/CN2014/075346 2013-07-03 2014-04-15 防松动螺纹件 WO2015000318A1 (zh)

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