WO2021057534A1 - 端面锥度定心互锁防松螺母套件 - Google Patents

端面锥度定心互锁防松螺母套件 Download PDF

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Publication number
WO2021057534A1
WO2021057534A1 PCT/CN2020/115197 CN2020115197W WO2021057534A1 WO 2021057534 A1 WO2021057534 A1 WO 2021057534A1 CN 2020115197 W CN2020115197 W CN 2020115197W WO 2021057534 A1 WO2021057534 A1 WO 2021057534A1
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WIPO (PCT)
Prior art keywords
boss
nut
hole
face
threaded
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PCT/CN2020/115197
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English (en)
French (fr)
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周峰
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周峰
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Application filed by 周峰 filed Critical 周峰
Publication of WO2021057534A1 publication Critical patent/WO2021057534A1/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
    • F16B39/02—Locking of screws, bolts or nuts in which the locking takes place after screwing down
    • F16B39/12—Locking of screws, bolts or nuts in which the locking takes place after screwing down by means of locknuts
    • F16B39/122—Locking of screws, bolts or nuts in which the locking takes place after screwing down by means of locknuts foreseen with mating surfaces inclined, i.e. not normal, to the bolt axis

Definitions

  • the invention relates to the field of fasteners, in particular to an end face taper centering interlocking anti-loosening nut kit.
  • the Japanese eccentric nut uses the eccentric taper surface to achieve the anti-vibration effect like a wedge wedged into the thread.
  • the eccentric nut has been widely used in the high-speed rail industry, convenient for disassembly and maintenance, and can be used multiple times.
  • the eccentric angle of the parallel offset will cause the lower nut to unidirectionally transmit the vibration force from the eccentric contact surface to the upper nut. Therefore, the full contact surface of the general nut will not cause the vibration to be evenly transmitted.
  • the nut is loose.
  • the eccentric taper surface of the eccentric nut is prone to generate additional lateral force applied to the thread during assembly, which affects the use effect or life of the thread.
  • the eccentric nut is generally subjected to lateral pressure
  • the screw is subjected to additional lateral force, which will cause the risk of fracture of the screw caused by the lateral force. Therefore, from a safety point of view, if the nut is not loose but the screw is broken, there is also a big safety hazard.
  • the invention provides a novel end-face taper centering interlocking anti-loosening nut kit that adopts end-face taper centering to avoid extra lateral force applied to the screw by the eccentricity, which avoids the lateral force of the thread caused by the eccentric taper side surface coordination, and its safety and anti-vibration
  • the performance is better than the existing anti-vibration nuts on the market.
  • an end-face taper centering interlocking lock nut kit comprising an upper nut with an axial threaded through hole I and a lower nut with an axial threaded through hole II, the threaded through hole I
  • the aperture of the upper nut is the same as the aperture of the threaded through hole II; one end of the upper nut is set as a boss, and the end of the boss has a taper; the one end of the lower nut is concavely formed with a corresponding boss A cylindrical groove, the central axis of the cylindrical groove coincides with the central axis of the threaded through hole II, and the contact plane between the bottom of the groove and the end surface of the boss is made with a taper that matches the end surface of the boss;
  • the end surface of the boss is located at the bottom of the groove, the central axis of the threaded through hole I coincides with the central axis of the threaded through hole II, the boss of the upper nut and
  • the profile design requirement of the boss is that there is a suspension at the contact plane between the bottom of the groove of the lower nut and the end surface of the boss of the upper nut.
  • the profile of the boss is one of an eccentric circle, an ellipse, a diamond, a perfect circle, a ring, or a triangle, or any shape.
  • a further technical solution may be: the profile of the boss is an eccentric circular shape eccentric to the axial threaded through hole I.
  • a further technical solution may be: the profile of the boss is a perfect circle concentric with the axial threaded through hole I, and the upper end surface of the boss is provided with a missing corner.
  • the end face taper centering interlocking anti-loosening nut kit of the present invention has the following beneficial effects:
  • the two sides of the upper and lower nut of the present invention have a clearance fit, and there is no side contact, so no additional lateral force is applied to the threaded working part, and it will never be affected by the lateral force.
  • the working condition is much better than that of Japanese eccentric nuts.
  • the eccentric boss of the Japanese eccentric nut still does not affect the assembly when the machining tolerance is small, but the radial force brought by the tolerance part to the thread will affect the service life and effect, even if the size is not excessive, it will still Interference squeezing produces additional lateral force applied to the thread.
  • the boss of the upper nut of the present invention and the cylindrical groove of the lower nut of the present invention have a cylindrical clearance fit on both sides (the eccentric or missing corner can be used to achieve the required unilateral down force), and it cannot be assembled at all when the size is out of tolerance. , From the root cause to eliminate the additional lateral force caused by the error to the thread.
  • the force-receiving surface acts on the end surface.
  • the force of the end taper of the present invention is not a centripetal force, but to prevent the upper and lower nuts from shifting and eccentricity after biting. Its main function is to center and try to ensure the coaxiality after the upper and lower nuts are screwed together. .
  • the eccentric design of the present invention (can also be designed into any shape: eccentric circle, rhombus, concentric circle, ring, ellipse, triangle, etc.) is mainly to produce a downward reverse direction when the nut under the groove is locked in a suspended place The pressure occludes the threaded surface at this place. The greater the pressure, the stronger the locking force and the better the anti-loosening performance.
  • the locking force of the present invention is the upper and lower locking force parallel to the axis.
  • the eccentric locking principle of Japanese eccentric nuts is that the protruding profile is pressed to generate centripetal force to lock, and the force generated by the locking is centripetal, not the up-and-down locking force of the present invention.
  • the present invention uses the profile of the upper and lower nuts to generate the upper and lower interlocking force coaxial with the screw to kill the screw thread surface, and all the stress points only act on the single-sided thread engagement surface, without any centripetal force affecting The strength of the screw; and because the upper and lower nuts have interlocking forces, the nut on the boss of the present invention can lock the parts with any torque.
  • the upper and lower nuts are interlocked. Do not follow the rotation of the upper nut until the required torque is reached, the axial force of the parts will not reach the limit of the screw, which can protect the screw and play a good anti-loosening effect.
  • this end-face taper centering interlocking lock nut kit is better than the centripetal force locking method of Japanese eccentric nuts, and it is also safer than the nut of the anti-loosing method that relies on high torque locking on the market.
  • the eccentric contact force surface of this nut kit is only on the end surface, and it is not like the Japanese eccentric nut.
  • the lateral pressure force makes the screw extra lateral force, which avoids the lateral force to the screw to the greatest extent.
  • the risk of fracture is better than that of Japanese eccentric nuts in terms of safety and anti-vibration effects.
  • the nut kit is convenient and reliable to install and easy to disassemble.
  • Figure 1 is a schematic view of the nut structure on the first embodiment
  • Figure 2 is a cross-sectional view of the nut on the first embodiment
  • Figure 3 is a perspective view of the nut on the first embodiment
  • FIG. 4 is a schematic diagram of the structure of the nut under the first embodiment
  • Figure 5 is a cross-sectional view of the nut under the first embodiment
  • Figure 6 is a perspective view of the nut under the first embodiment
  • Figure 7 is a schematic diagram of the assembly of the upper nut and the lower nut in the first embodiment
  • Fig. 8 is a diagram of the use state of the end-face taper centering interlocking anti-loosening nut kit according to the first embodiment of the present invention.
  • Figure 9 is a schematic diagram of the nut structure on the second embodiment.
  • Figure 10 is a cross-sectional view of the nut on the second embodiment
  • Figure 11 is a perspective view of the nut on the second embodiment
  • Figure 12 is a schematic view of the nut structure under the second embodiment
  • Figure 13 is a cross-sectional view of the nut under the second embodiment
  • Figure 14 is a perspective view of the nut under the second embodiment
  • 15 is a schematic diagram of the assembly of the upper nut and the lower nut of the second embodiment
  • Fig. 16 is a diagram of the use state of the end-face taper centering interlocking anti-loosening nut kit of the second embodiment of the present invention.
  • An end face taper centering and interlocking lock nut kit includes an upper nut with an axial threaded through hole I and a lower nut with an axial threaded through hole II.
  • the diameter of the threaded through hole I is the same as the threaded through hole II.
  • the aperture is the same; one end surface of the upper nut is set as a boss, and the end surface of the boss has a taper; one end surface of the lower nut is concavely formed with a cylindrical groove adapted to the boss, the The central axis of the cylindrical groove coincides with the central axis of the threaded through hole II, and the contact plane between the bottom of the groove and the end face of the boss is made into a taper that matches the end face of the boss; in the assembled state, the boss The end surface is located at the bottom of the groove, the central axis of the threaded through hole I coincides with the central axis of the threaded through hole II, and the boss of the upper nut is in clearance fit with the cylindrical groove of the lower nut.
  • the profile design requirement of the boss is that there is a suspension at the contact plane between the bottom of the groove of the lower nut and the end surface of the boss of the upper nut.
  • the present invention uses a specific boss profile (not limited to any shape such as eccentric circle, ellipse, rhombus, perfect circle, ring, triangle, etc.) to make the upper and lower nuts produce a unilateral depression interlocking force, and the taper end surface is used for setting. It is the scope of the patent protection of the present invention that the screw thread surface can be locked and cannot be rotated and exited.
  • the invention has also passed a large number of actual tests to conclude that any type of fit, as long as the principle of the invention can be followed, can obtain good anti-loose performance, and can completely pass the GB/T10431 (2008) transverse vibration test. It can continue until the fatigue fracture of the screw is still not loosened.
  • an end-face taper centering interlocking locknut kit includes an upper nut I1 with an axially threaded through hole Ia12 and a lower nut I2 with an axially threaded through hole IIa.
  • the thread The hole diameter of the through hole Ia12 is the same as the hole diameter of the threaded through hole IIa22.
  • One end surface of the upper nut I1 is set as a circular boss I11, and the profile of the circular boss I11 is an eccentric circle eccentric to the axial threaded through hole Ia12, as shown in Figure 1, where a represents The center line of the circular boss I11, b in the figure represents the center line of the axial threaded through hole Ia12; the end surface A of the circular boss I11 (see Figure 2 and Figure 3) has a taper.
  • One end surface of the lower nut I2 is concavely formed with a cylindrical groove I21 that is compatible with the circular boss I11.
  • the central axis of the cylindrical groove I21 coincides with the central axis of the threaded through hole IIa, so
  • the contact plane B (see Figure 5) between the bottom of the cylindrical groove I21 and the end surface of the circular boss is made into a taper that matches the end surface of the circular boss I11.
  • the end surface of the circular boss I11 is located at the bottom of the cylindrical groove I21, the central axis of the threaded through hole Ia12 coincides with the central axis of the threaded through hole IIa22, and the circular convexity of the upper nut I
  • the table I11 is in clearance fit with the cylindrical groove I21 of the lower nut I.
  • the focus of this embodiment is that the end-face taper centering allows the unidirectional locking force caused by eccentricity to be applied only to the single-sided thread after the locking force, without additional application to the screw to produce a laterally centripetal side.
  • the force protects the screw to the greatest extent and avoids the risk of screw fracture to the greatest extent.
  • an end-face taper centering interlocking locknut kit includes an upper nut II3 with an axially threaded through hole Ib32 and a lower nut II4 with an axially threaded through hole IIb42.
  • the thread The hole diameter of the through hole Ib32 is the same as the hole diameter of the threaded through hole IIb42.
  • One end surface of the upper nut II3 is set as a circular boss II31, the profile of the circular boss II31 is a perfect circle concentric with the axial threaded through hole Ib32, and the upper part of the circular boss II31 A missing corner 33 is provided on the end face.
  • c in the figure represents the center line of the circular boss II 31, and also the center line of the threaded through hole II b42.
  • the center line of the circular boss II 31 coincides with the center line of the threaded through hole II b42;
  • the end surface C of the circular boss II 31 see Fig. 10 and Fig.
  • one end surface of the lower nut II 4 is concavely formed with a cylindrical groove II 41 that is compatible with the circular boss II 31.
  • the central axis of the shaped groove II coincides with the central axis of the threaded through hole IIb42, and the contact plane D (see Figure 13) between the bottom of the cylindrical groove II 41 and the end surface of the circular boss is made with the circular boss Matching taper of II31 end face.
  • the end surface of the circular boss II31 is located at the bottom of the cylindrical groove II41, the central axis of the threaded through hole Ib32 coincides with the central axis of the threaded through hole IIb42, and the circular convex of the upper nut II3
  • the table II31 is in clearance fit with the cylindrical groove II41 of the lower nut II4.
  • the focus of this embodiment is that the end-face taper centering allows the unidirectional locking force caused by the missing angle to be applied to the single-sided thread only, instead of being applied to the laterally centripetal side of the screw.
  • Directional force protects the screw to the greatest extent and avoids the risk of screw fracture to the greatest extent.
  • the above two embodiments ensure that no lateral force is applied to the screw through the taper of the end surface, and use eccentricity or missing angle to cause the groove nut to generate a downward unidirectional locking force in the suspended position to kill the thread profile. Anti-loose effect.
  • use eccentricity or missing angle to make the upper and lower nuts produce axial unilateral interlocking force after locking to lock the thread, and the taper of the end surface is matched with the centering to prevent lateral slippage in the process of thread locking.
  • the centripetal force causes the screw to withstand additional lateral force.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Connection Of Plates (AREA)
  • Clamps And Clips (AREA)

Abstract

一种端面锥度定心互锁防松螺母套件，包括具有轴向螺纹通孔I(12,32)的上螺母（1,3）和具有轴向螺纹通孔II（22,42）的下螺母（2,4），上螺母的一端面设置为一凸台（11,31），凸台的端面具有锥度；下螺母的一端面内凹成型有一与凸台相适应的圆柱形的凹槽（21,41），凹槽底部与凸台端面的接触平面处制成与凸台端面相适配的锥度；装配状态下，凸台的端面位于凹槽的底部，螺纹通孔I的中心轴与螺纹通孔II中心轴重合，上螺母的凸台与下螺母的圆柱形的凹槽为间隙配合。本螺母套件采用端面锥度定心避免偏心给螺杆（5）额外施加侧向力的新型端面锥度定心互锁防松螺母套件，避免了偏心锥侧面配合导致螺纹侧向受力。

Description

端面锥度定心互锁防松螺母套件
 
技术领域
本发明涉及紧固件领域，具体是端面锥度定心互锁防松螺母套件。
背景技术
日本的偏心螺母利用的是偏心的锥度面配合达到类似楔子楔入螺纹内的防震作用。该偏心螺母已经广泛应用在高铁行业了，方便拆卸维修，可多次使用。当上下螺母锁紧后，因为平行偏移的偏心角度会让下螺母将震动力从偏心接触面上单向传递给上螺母，因此，不会发生一般螺母的全接触面导致震动均匀传递而造成螺母松动。但是，偏心螺母的偏心锥度面在装配时容易产生额外施加给螺纹侧向力，影响螺纹使用效果或者寿命。还会因为偏心螺母一般是侧向施压受力令螺杆额外承受侧向力，会造成侧向力给螺杆带来的断裂风险。因此从安全角度来说，螺母不松动但螺杆断裂了，也存在很大的安全隐患。
发明内容
    本发明提供一种采用端面锥度定心避免偏心给螺杆额外施加侧向力的新型端面锥度定心互锁防松螺母套件，避免了偏心锥侧面配合导致螺纹侧向受力，其安全性及抗震性能均优于现有市面上的防震螺母。
本发明采取的技术方案是：一种端面锥度定心互锁防松螺母套件，包括具有轴向螺纹通孔Ⅰ的上螺母和具有轴向螺纹通孔Ⅱ的下螺母，所述螺纹通孔Ⅰ的孔径与螺纹通孔Ⅱ的孔径相同；所述上螺母的一端面设置为一凸台，所述凸台的端面具有锥度；所述下螺母的一端面内凹成型有一与凸台相适应的圆柱形的凹槽，所述圆柱形的凹槽的中心轴与螺纹通孔Ⅱ的中心轴重合，所述凹槽底部与凸台端面的接触平面处制成与凸台端面相适配的锥度；装配状态下，所述凸台的端面位于凹槽的底部，所述螺纹通孔Ⅰ的中心轴与螺纹通孔Ⅱ中心轴重合，所述上螺母的凸台与下螺母的圆柱形的凹槽为间隙配合。
其进一步技术方案是：所述凸台的型面设计要求是：下螺母的凹槽底部与上螺母的凸台端面的接触平面处存在悬空。
    其更进一步技术方案是：所述凸台的型面为偏心圆形、椭圆、菱形、正圆、环形、三角形中的一种或为任意一种形状。
其更进一步技术方案或是：所述凸台的型面是与轴向螺纹通孔Ⅰ偏心的偏心圆形。
其更进一步技术方案或是：所述凸台的型面是与轴向螺纹通孔Ⅰ同心的正圆形，且所述凸台的上端面设置有一缺角。
由于采取上述技术方案，本发明之端面锥度定心互锁防松螺母套件具有如下有益效果：
对比当前偏心螺母的工作原理，本发明的上下螺母两侧面是间隙配合，并没有侧面的接触，也就没有产生额外的侧向力施加给螺纹工作部分，绝对不会因为侧向受力而影响到螺纹的疲劳强度及啮合力，工作状况大大优于日本偏心螺母。日本偏心螺母的偏心凸台在加工超差较少的时候依然不影响装配，但超差部分给螺纹带来的径向力是会影响使用寿命及效果的，即便尺寸完全不超差，依然会有过盈挤压产生额外的侧向力施加给螺纹。而本发明的上螺母的凸台与下螺母的圆柱形的凹槽两侧面是圆柱形间隙配合（可利用偏心或者缺角达到所需的单侧下压力），当尺寸超差时根本无法装配，从根源上杜绝了因误差而给螺纹带来额外的侧向受力。
并且，本发明中，螺母上下型面贴合的时候，受力面是作用于端面的。对比日本偏心螺母发现，本发明的端面锥度其作用力并不是一个向心力，而是为了防止上下螺母咬合后发生偏移偏心，其主要作用是定心，尽量保证上下螺母旋合后的同轴度。因此本发明的偏心设计（也可以设计成任意形状：偏心圆形、菱形、同心圆、环形、椭圆、三角形等等）主要是以悬空处令凹槽下螺母锁紧时产生向下的反向压力咬死该处的螺纹面，压力越大，锁紧力越强，防松性能越优异，本发明的锁紧力是平行于轴心的上下锁紧力。而日本偏心螺母的偏心锁紧原理是以突出的型面受压产生向心力去锁紧，其锁紧产生的力是向心的，而非本发明的上下锁紧力。本发明这种利用上下螺母的型面产生与螺杆同轴的上下互锁力咬死螺杆的螺纹面，所有的受力点均只作用于单侧螺纹啮合面，而不产生任何的向心力影响到螺杆的强度；又因上下螺母是有互锁的力，因此，本发明的凸台上螺母可以任意力矩锁紧零件，拧入凹槽下螺母锁紧的时候上下螺母产生互锁，下螺母并不跟随上螺母转动，直至拧到所需扭矩后，零件所承受的轴力并不会达到螺杆承受的极限，既能保护螺杆又能起到良好的防松效果。因此本端面锥度定心互锁防松螺母套件安全性能较日本偏心螺母的向心力锁紧方式更优异，也同比市面上依靠大扭矩锁紧的防松方式的螺母更安全。
综上所述，本螺母套件的偏心接触受力面仅仅在于端面，并没有如日本偏心螺母一般是侧向施压受力令螺杆额外承受侧向力，最大程度上避免了侧向力给螺杆带来的断裂风险，无论从安全性还是防震效果均优于日本偏心螺母。并且本螺母套件安装方便可靠，拆卸简单。
下面结合附图和实施例对本发明之端面锥度定心互锁防松螺母套件的技术特征作进一步说明。
附图说明
图1是实施例一之上螺母结构示意图；
图2是实施例一之上螺母剖视图；
图3是实施例一之上螺母立体图；
图4是实施例一之下螺母结构示意图；
图5是实施例一之下螺母剖视图；
图6是实施例一之下螺母立体图；
图7是实施例一之上螺母与下螺母装配示意图；
图8是实施例一本发明端面锥度定心互锁防松螺母套件使用状态图。
图9是实施例二之上螺母结构示意图；
图10是实施例二之上螺母剖视图；
图11是实施例二之上螺母立体图；
图12是实施例二之下螺母结构示意图；
图13是实施例二之下螺母剖视图；
图14是实施例二之下螺母立体图；
图15是实施例二之上螺母与下螺母装配示意图；
图16是实施例二本发明端面锥度定心互锁防松螺母套件使用状态图。
图中：
1-上螺母Ⅰ，11-圆形凸台Ⅰ，12-螺纹通孔Ⅰa；
2-下螺母Ⅰ，21-圆柱形的凹槽Ⅰ，22-螺纹通孔Ⅱa；
3-上螺母Ⅱ，31-圆形凸台Ⅱ，32-螺纹通孔Ⅰb，33-缺角；
4-下螺母Ⅱ，41-圆柱形的凹槽Ⅱ，42-螺纹通孔Ⅱb；
5-螺杆。
具体实施方式
 一种端面锥度定心互锁防松螺母套件，包括具有轴向螺纹通孔Ⅰ的上螺母和具有轴向螺纹通孔Ⅱ的下螺母，所述螺纹通孔Ⅰ的孔径与螺纹通孔Ⅱ的孔径相同；所述上螺母的一端面设置为一凸台，所述凸台的端面具有锥度；所述下螺母的一端面内凹成型有一与凸台相适应的圆柱形的凹槽，所述圆柱形的凹槽的中心轴与螺纹通孔Ⅱ的中心轴重合，所述凹槽底部与凸台端面的接触平面处制成与凸台端面相适配的锥度；装配状态下，所述凸台的端面位于凹槽的底部，所述螺纹通孔Ⅰ的中心轴与螺纹通孔Ⅱ中心轴重合，所述上螺母的凸台与下螺母的圆柱形的凹槽为间隙配合。
所述凸台的型面设计要求是：下螺母的凹槽底部与上螺母的凸台端面的接触平面处存在悬空。
本发明通过特定的凸台型面（可不限于偏心圆形、椭圆、菱形、正圆、环形、三角形等任意形状）使得上下螺帽产生单侧下压的互锁力，并通过锥度端面进行定心，就可以将螺杆的螺纹面锁死无法旋转退出均为本发明的专利保护范围。本发明也通过了大量的实际测试得出结论，任意型面配合，只要能遵循本发明的原理，均可以获得良好的防松性能，完全能通过GB/T10431(2008)横向振动试验检测，试验可以持续到螺杆疲劳断裂依然毫无松动。
下面通过凸台型面为偏心圆形及同心圆两种比较典型的外观的实施例方式进一步说明本发明，但并不因此将本发明限制在所述的实施例范围之中。
实施例一：
如图1至图7所示，一种端面锥度定心互锁防松螺母套件，包括具有轴向螺纹通孔Ⅰa12的上螺母Ⅰ1和具有轴向螺纹通孔Ⅱa的下螺母Ⅰ2，所述螺纹通孔Ⅰa12的孔径与螺纹通孔Ⅱa22的孔径相同。
所述上螺母Ⅰ1的一端面设置为一圆形凸台Ⅰ11，该圆形凸台Ⅰ11的型面是与轴向螺纹通孔Ⅰa12偏心的偏心圆形，如图1所示，图中a表示圆形凸台Ⅰ11的中心线，图中b表示轴向螺纹通孔Ⅰa12的中心线；所述圆形凸台Ⅰ11的端面A（参见图2、图3）具有锥度。
所述下螺母Ⅰ2的一端面内凹成型有一与圆形凸台Ⅰ11相适应的圆柱形的凹槽Ⅰ21，所述圆柱形的凹槽Ⅰ21的中心轴与螺纹通孔Ⅱa的中心轴重合，所述圆柱形的凹槽Ⅰ21底部与圆形凸台端面的接触平面处B（参见图5）制成与圆形凸台Ⅰ11端面相适配的锥度。
装配状态下，所述圆形凸台Ⅰ11的端面位于圆柱形的凹槽Ⅰ21的底部，所述螺纹通孔Ⅰa12的中心轴与螺纹通孔Ⅱa22中心轴重合，所述上螺母Ⅰ的圆形凸台Ⅰ11与下螺母Ⅰ的圆柱形的凹槽Ⅰ21的间隙配合。从图7中可知，图中E处显示的是圆柱形的凹槽Ⅰ21和圆形凸台Ⅰ11的两侧面是间隙配合，无过盈挤压导致的侧向受力；图中F处显示的是锥度端面（A、B）配合确保锁紧后同轴不发生偏移；图中G处显示的是偏心导致此处悬空，紧锁力集中此处令上下螺母单向夹紧螺杆螺纹面；图中f1表示紧锁后产生的向上推力，推力的方向为箭头所指的方向；图中f2表示悬空导致产生单侧向下压力，压力的方向为箭头所指的方向。本实施例的端面锥度定心互锁防松螺母套件使用状态参见图8。
本实施例的重点是端面锥度定心可以让因偏心导致的单向锁紧力锁紧后的作用力仅仅施加于单侧螺纹上，而不会额外的施加给螺杆产生横向向心的侧向力，最大程度的保护了螺杆，最大限度避免了螺杆断裂的风险。
实施例二：
如图9至图15所示，一种端面锥度定心互锁防松螺母套件，包括具有轴向螺纹通孔Ⅰb32的上螺母Ⅱ3和具有轴向螺纹通孔Ⅱb42的下螺母Ⅱ4，所述螺纹通孔Ⅰb32的孔径与螺纹通孔Ⅱb42的孔径相同。
所述上螺母Ⅱ3的一端面设置为一圆形凸台Ⅱ31，该圆形凸台Ⅱ31的型面是与轴向螺纹通孔Ⅰb32同心的正圆形，且所述圆形凸台Ⅱ31的上端面设置有一缺角33。如图9所示，图中c表示圆形凸台Ⅱ31的中心线，亦表示螺纹通孔Ⅱb42的中心线，该圆形凸台Ⅱ31的中心线与螺纹通孔Ⅱb42的中心线重合；所述圆形凸台Ⅱ31的端面C（参见图10、图11）具有锥度；所述下螺母Ⅱ4的一端面内凹成型有一与圆形凸台Ⅱ31相适应的圆柱形的凹槽Ⅱ41，所述圆柱形的凹槽Ⅱ的中心轴与螺纹通孔Ⅱb42的中心轴重合，所述圆柱形的凹槽Ⅱ41底部与圆形凸台端面的接触平面处D（参见图13）制成与圆形凸台Ⅱ31端面相适配的锥度。
装配状态下，所述圆形凸台Ⅱ31的端面位于圆柱形的凹槽Ⅱ41的底部，所述螺纹通孔Ⅰb32的中心轴与螺纹通孔Ⅱb42中心轴重合，所述上螺母Ⅱ3的圆形凸台Ⅱ31与下螺母Ⅱ4的圆柱形的凹槽Ⅱ41为间隙配合。从图15中可知，图中H、I两处显示的是圆柱形的凹槽Ⅱ41和圆形凸台Ⅱ31的两侧面是间隙配合，无过盈挤压导致的侧向受力；图中J处显示的是圆形凸台Ⅱ31缺角悬空导致缺角单侧受压大于无缺角方向；图中K处显示的是锥度端面（C、D）配合确保锁紧后同轴不发生偏移；图中f1表示紧锁后产生的向上推力，推力的方向为箭头所指的方向；图中f2表示悬空导致产生单侧向下压力，压力的方向为箭头所指的方向。本实施例的使用状态参见图16。
本实施例的重点是端面锥度定心可以让因缺角导致的单向锁紧力锁紧后的作用力仅仅施加于单侧螺纹上，而不会额外的施加给螺杆产生横向向心的侧向力，最大程度的保护了螺杆，最大限度避免了螺杆断裂的风险。
上述的两个实施例通过端面的锥度定心，保证无侧向力施加给螺杆，利用偏心或者缺角使得凹槽螺母于悬空处产生向下的单向锁紧力咬死螺纹型面起到防松效果。换一种说法是利用偏心或者缺角使得上下螺母在锁紧后产生轴向的单侧互锁力锁死螺纹，并通过端面的锥度配合定心防止螺纹锁死过程中的侧向滑移产生向心力导致螺杆承受额外侧向力。
本发明未涉及部分均与现有技术相同或可采用现有技术加以实现。以上内容是结合具体的优选实施方式对本发明所作的进一步详细说明，不能认定本发明的具体实施只局限于上述各实施例的记载，对于本发明所属技术领域的普通技术人员来说，在不脱离本发明构思的前提下，还可以做出若干简单推演或替换，都应当视为属于本发明由所提交的权利要求书确定的专利保护范围。

Claims (5)

  1. 一种端面锥度定心互锁防松螺母套件，其特征在于：包括具有轴向螺纹通孔Ⅰ的上螺母和具有轴向螺纹通孔Ⅱ的下螺母，所述螺纹通孔Ⅰ的孔径与螺纹通孔Ⅱ的孔径相同；所述上螺母的一端面设置为一凸台，所述凸台的端面具有锥度；所述下螺母的一端面内凹成型有一与凸台相适应的圆柱形的凹槽，所述圆柱形的凹槽的中心轴与螺纹通孔Ⅱ的中心轴重合，所述凹槽底部与凸台端面的接触平面处制成与凸台端面相适配的锥度；装配状态下，所述凸台的端面位于凹槽的底部，所述螺纹通孔Ⅰ的中心轴与螺纹通孔Ⅱ中心轴重合，所述上螺母的凸台与下螺母的圆柱形的凹槽为间隙配合。
  2. 根据权利要求1所述的端面锥度定心互锁防松螺母套件，其特征在于：所述凸台的型面设计要求是：下螺母的凹槽底部与上螺母的凸台端面的接触平面处存在悬空。
  3. 根据权利要求2所述的端面锥度定心互锁防松螺母套件，其特征在于：所述凸台的型面为偏心圆形、椭圆、菱形、正圆、环形、三角形中的一种或为任意一种形状。
  4. 根据权利要求3所述的端面锥度定心互锁防松螺母套件，其特征在于：所述凸台的型面是与轴向螺纹通孔Ⅰ偏心的偏心圆形。
  5. 根据权利要求3所述的端面锥度定心互锁防松螺母套件，其特征在于：所述凸台的型面是与轴向螺纹通孔Ⅰ同心的正圆形，且所述凸台的上端面设置有一缺角。
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