WO2019131685A1 - Écrou de fixation - Google Patents

Écrou de fixation Download PDF

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Publication number
WO2019131685A1
WO2019131685A1 PCT/JP2018/047682 JP2018047682W WO2019131685A1 WO 2019131685 A1 WO2019131685 A1 WO 2019131685A1 JP 2018047682 W JP2018047682 W JP 2018047682W WO 2019131685 A1 WO2019131685 A1 WO 2019131685A1
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WO
WIPO (PCT)
Prior art keywords
nut
film
screw
thread
bolt
Prior art date
Application number
PCT/JP2018/047682
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English (en)
Japanese (ja)
Inventor
松尾　誠
興明 林田
喜直 岩本
Original Assignee
株式会社松尾工業所
株式会社iMott
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Application filed by 株式会社松尾工業所, 株式会社iMott filed Critical 株式会社松尾工業所
Priority to JP2019562057A priority Critical patent/JP7141622B2/ja
Publication of WO2019131685A1 publication Critical patent/WO2019131685A1/fr

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    • 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
    • F16B31/00—Screwed connections specially modified in view of tensile load; Break-bolts
    • F16B31/02—Screwed connections specially modified in view of tensile load; Break-bolts for indicating the attainment of a particular tensile load or limiting tensile load
    • 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
    • F16B33/00—Features common to bolt and nut
    • F16B33/06—Surface treatment of parts furnished with screw-thread, e.g. for preventing seizure or fretting
    • 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
    • F16B37/00—Nuts or like thread-engaging members

Definitions

  • the present invention relates to a nut used in bolt and nut fastening, and for the purpose of reducing the load on the fastening meshing first peak thread.
  • the screw fastening part of the conventional method has the smallest cross-sectional area and the largest load sharing due to the application of repeated external load during use on the initial fastening load.
  • the fatigue failure strength is the lowest at the part. It is known that many cracked axial fractures occur at this location.
  • Patent Documents 1 and 3 disclose a bolt characterized in that the bolt thread to be fitted is tapered in the tensile direction of the bolt and the bolt thread is obliquely cut low, and is directed in the axial direction. The intention is to reduce the contact area between the bolt thread and the nut thread sequentially and to equalize the load from the nut thread on the bolt thread to improve the fatigue life. It is stated that this forming process may be performed on the nut, but no description or figure is shown.
  • Patent Document 4 discloses a nut characterized in that one or both of the slope angles of the thread of the nut fitted to the bolt is smaller than the slope angle of the bolt, and It has been disclosed that the contact area of the thread of the nut is reduced to equalize the load applied to the thread and improve the fatigue life.
  • Patent Document 2 discloses a method of manufacturing a bolt in which a threaded portion of a bolt material is formed into a tapered shape in the direction of tensile force application, and subsequently, threading with a uniform valley diameter is performed.
  • Patent Document 5 in a steel bolt in which the pitch of the bolt is smaller than the pitch of the nut, the pitch difference is in the range of 0.5 to 0.8% of the pitch tolerance specified in Japanese Industrial Standard JIS B 0205
  • a steel bolt is disclosed which is characterized in that it is designed to provide offsets, avoiding simultaneous contact of the screw faces, and as the fastening progresses and the screw thread is deformed by stress, the stress transfer position is sequentially
  • a structure is disclosed that travels and receives a full load.
  • Patent Documents 1 to 5 have a problem that the screw shape is out of the standard such as JIS or ISO because they are processed on the screw threads of these bolts and nuts, and these are basically bolts
  • the threading position is made into a dedicated part by the thickness, structure, etc. of the object to be fastened, and it is necessary to apply thread thread forming processing of the bolt to a position which becomes a specific size for each object to be fastened ,
  • These bolts are not versatile.
  • Patent Documents 6 to 8 propose a set of a bolt, a nut and a washer in a high strength nut for friction bonding in relation to the nut side, and Patent Document 6 in the following.
  • a first structural example of this set is described in FIGS. 1 and 2 of the patent document. It is stated that what is important in the set of bolts, nuts and washers is to reduce the variation in torque coefficient, and therefore curved projections are formed on the outer peripheral side of the end face on the washer side of the nut to facilitate penetration into the washer. And a structure in which a receding surface and an annular groove are formed on the inner peripheral portion.
  • the projections formed on the seat surface and the receding surface relieve the stress concentration on the first thread of the screw at the time of fastening, and further the effect is enhanced by the annular groove.
  • the use of an effective lubricant is affected as the bolt axial force is affected by the lubricating performance of the contact portion between the nut and the washer and the lubricating performance between the nut screw and the bolt screw.
  • the curved projections on the nut bearing surface do not apply, and a normal planar bearing surface does not apply, and the structure as a nut, the shape of the annular groove essentially related to the stress concentration relaxation characteristics, in particular There is no description about the depth.
  • the effect of relieving stress concentration is indicated by the magnitude of the variation in torque coefficient, but the intrinsic structure and characteristics of the combination of bolt and nut, which is the effect of lubricant, protrusion, receding surface, or groove Even though it is a relation of Inherently, the variation in torque coefficient is derived from the friction state at the screw thread or bearing surface, the material of the bolt and the hardness, and this is a factor different from the purpose of reducing the load concentration of the first tightening.
  • Patent Document 6 adopts a fastening method and a purpose that is largely different from a normal bolt and a nut fastening method in which fastening is performed while rotating the nut.
  • a convex protrusion is provided on the nut bearing surface to bite into the object to be fastened. It is the part that claims to "improved the nut having the flat surface so far".
  • FIG. 7 of Patent Document 6 A separate part is inserted into the outer periphery of the hexagonal nut, but this separate part is a kind of sleeve-like structure that is fitted to the inner hexagonal nut and can not be rotated relative to the inner hexagonal nut, and on the washer side It is characterized in that a curved projection is provided.
  • the assumed fastening action at the time of fastening is the same as in the first structural example, and the force from the seat surface enters the curved surface-like protrusion of this chevron, and the chevron curved surface-like protrusion deforms the other seat surface Later, it enters the flange portion of the inner nut upper part.
  • Patent Document 7 as a shear delayed fracture preventing nut, in order to make uniform shear stress acting on a screw thread of a bolt and a nut, a rotational parachute gap at the tip of the bolt and a nut A combination of flange lip and nut has been proposed.
  • the longitudinal cross section of the nut of Patent Document 7 is provided with a threadless portion (11 in FIG. 1) on the upper inner diameter side, and an oblique wedge-shaped lip is at the same height as the depth without the thread. It is intruding. For this reason, the height direction dimensions of the inner corner of the recess 11 without screw and the innermost part of the wedge-shaped lip outside the screw ridge are "height of the wedge-shaped lip from the object to be fastened ⁇ ⁇ space without screw It is the height to the bottom of 11 ".
  • patent document 7 states that "the prevention of shear delayed breakage of a bolt" is established at this time, it is necessary to put the wedge-shaped lip to the vicinity of the top of the nut when there is this purpose.
  • Patent Document 8 proposes a nut having a large R (a spherical surface in which the inside is recessed) in a washer and a similar R bearing surface.
  • the washer has a larger outer diameter than the nut, and when the surface of the part to be fastened under the washer is slightly inclined, or when the surface condition is uneven or unstable, tightening the nut against the bolt
  • the structure shows that the washer-like substrate uniformly contacts the nut bearing surface, and fastening can be performed even when the surface of the object to be fastened is unstable.
  • the washer has a larger outer diameter than the nut but no mention is made of the central bore diameter. The effect and structure leading to the reduction of the load on the bottom of the bolt thread in the first engagement are not disclosed, and the purpose is different from the present invention.
  • JP-A-52-79163 JP-A-52-131060 U.S. Pat. No. 4,189,975 JP-A-58-160613 JP 2005-265150 A Unexamined-Japanese-Patent No. 5-288209 Japanese Patent Laid-Open No. 2002-61619 Japanese Patent Application Laid-Open No. 1-182614
  • FIG. 4 is a longitudinal sectional view of a general fastening of a conventional flange nut.
  • the screw threads of the flange nut 1 are substantially uniformly formed according to JIS B 0205 (ISO 724) from the fastening side to the open side.
  • JIS B 0205 ISO 724
  • 1 is a conventional flange nut main body
  • 2 is a bolt
  • 3 is an object to be fastened
  • 8 is a screw thread side of a nut thread
  • 8a is an end face of a screw thread side of a nut thread and a nut bearing surface
  • 9a is the open end face of the nut thread
  • 14 is the nut bearing surface
  • 15 is the conventional thread valley bottom
  • 17 is the outer periphery of the nut
  • 19 is the nut thread.
  • the threaded portion of the bolt 2 is screwed into the threaded portion of the nut 1 to clamp the washer 23 and clamp the object 3 to be fastened.
  • FIG. 4 shows the conventional fastening state, and the nut 1 fastens the object 3 via the washer 23.
  • the bolt 2 penetrates the screw hole from below and is fastened to the nut.
  • Figure 4-1 (a) shows the Mises equivalent stress distribution of the nut (seven screw thread) same as Figure 4 (Maximum of thread valley bottom marked with * on the left side of the first ridge of bolt (No. 1) Indicates where stress is applied and crack axis fracture is likely to occur).
  • the force entered from the nut bearing surface 14 is directed in the direction of pushing up the nearest bolt thread No. 1 and the bolt is most strongly pulling the No. 1 peak by the axial force, so the part * becomes open ing.
  • Fig. 4-2 is a vector diagram of the Mises equivalent stress and shows what kind of force is flowing to the bolt at the maximum principal stress (tensile stress), and Fig. 4-3 also shows the minimum principal stress (compressive stress) at the vector diagram. Indicated here is the flow of force in the nut. Also in this vector diagram, it can be seen that the power is concentrated in the meshing first mountain.
  • FIG. 4-1 (b) shows the Mises equivalent stress distribution map of screw 8 and Figure 4-1 (c) shows the Mises equivalent stress distribution of 9 screw threads, comparing these load sharing ratios with 7 Figure 4-4 (a) (conventional nut (load distribution ratio comparison chart for 7, 8 and 9 threads) is displayed, and a comparison bar graph of these three load distribution ratios is shown in Figure 4-4 (b).
  • the load sharing ratio to mesh 1 is 36.5% at 7 mountains, 34.5% at 8 mountains, 33.4% at 9 mountains
  • the number of screw threads is 7 mountains.
  • 8 mountains and 9 mountains excessive stress is applied to the bolt side meshing first valley thread valley bottom of ⁇ part in Fig. 4-1 (a), (b), (c) This result indicates that the reduction effect of the meshing first peak load is small even if the number of threads of the conventional type nut is increased.
  • the bolt and the bolt are tightened by reducing the load on the first mesh meshing engagement. It is possible to provide a nut that improves the fatigue fracture life of the cracked axis fracture from the bottom of meshed first valley which is the strength weakest part.
  • the present invention provides the following inventions in order to solve the above-mentioned problems. That is, by increasing the load sharing after the third opening side by setting the nut structure to make the flow of the force of the load received by the nut more directed to the open side meshing thread with low load sharing, the meshing can be achieved.
  • a nut having a structure characterized in that load concentration on a first peak is reduced.
  • a convex-shaped space is concentrically formed on the bearing surface on the nut fastening side around the axis of the screw, and the space is connected by a straight line, a curve or a combination thereof.
  • It is a structure in which a space is formed as a shape, and the depth from the bearing surface of the space is L 2 , and the axial length from the first valley bottom of the fully threaded portion of the nut to the bearing surface is L 1 , By forming the space with the depth L 2 of the space as L 1 ⁇ L 2 ⁇ L 1 + length of 5 threads of the screw thread; B.
  • the recess has an inner wall and a curve, straight line, or the like rising perpendicularly from the nut bearing surface
  • a nut having a two-part structure comprising a nut body having a screw shaft portion provided with a screw thread inside and a flange bearing surface portion and a pipe-like nut component having a chamfered bearing surface on at least one end face inner diameter side
  • a shape of a longitudinal sectional view of the nut body is T-shaped, and a length in which a screw shaft portion of the nut body is introduced from the flange seat surface portion of the nut body toward the inner object of the nut component is
  • the hollow pipe-shaped nut component is formed on the outer surface of the screw outer surface so that the incomplete screw part length s + the length of the screw pitch 0.5 or more, and the length of the incomplete screw part s + the screw pitch 5 m or less
  • the T-shaped nut body is disposed so that the lowermost portion of the T-shaped nut body is not in contact with the object, and the uppermost portion
  • Diamond-like carbon (DLC) film BN film, WC film, WC film, CrN film, HfN film, VN film, TiN film, TiCN film, Al 2 O 3 film on both or one side of the contact surface of nut body and nut part ZnO film, SiO 2 film, alumite, metal plating, polymer resin coating, solid lubricating layer, manganese phosphate chemical conversion treatment, carburizing and quenching, nitriding treatment, chromium treatment, or any combination thereof
  • the nut according to any one of (1) to (2).
  • a SiO 2 film, alumite, metal plating, polymer resin coating, solid lubricating layer, manganese phosphate conversion treatment, carburizing and quenching, nitriding treatment, chromiumizing treatment, or a combination thereof is coated (1) to Providing the nut as described in any of (3).
  • the force applied from the nut bearing surface is directed to the open side thread after the third mesh and more load is shared.
  • the load concentration on the meshing first peak can be reduced, and this effect leads to the improvement of the fatigue fracture life of the cracked axis fracture of the bolt valley bottom of the meshing first peak.
  • a nut structure in which "flow of force" is more frequently directed to the third and subsequent open side As a method, changing the external shape and structure of the nut without changing the JIS (ISO) standard of the screw thread shape of the nut, that is, optimizing the structure to obtain the force of the nut It can be directed to the open side screw after the third peak.
  • ISO JIS
  • the above-mentioned screw meshing first ridge is, for example, a screw thread indicated by a symbol 1 shown in a bolt and a nut of the conventional method shown in FIG.
  • the side of the first thread of the nut loads and fastens the side of the first thread of the bolt.
  • the "first thread" of the nut is on the fastening side and the thread is the first fully threaded part having a normal thread shape.
  • the above-mentioned incomplete thread portion is a portion having a length including about one pitch and a chamfer from the start of thread cutting.
  • the position of the first thread of the nut is the first peak of the complete thread.
  • the screw thread of the bolt engaged with the first screw thread of the nut is the first screw thread of the bolt, and the first valley bottom of the bolt is located on the fastening side of the first screw thread of the bolt.
  • the screw shape of the nut of the present invention preferably conforms to that defined in JIS B 0205 (ISO 724). Also, the configuration of the nut of the present invention is also applied to a nut having a thread shape which is widely used conventionally, such as an inch screw, for example, and these are also part of the present invention.
  • the load sharing of the fastening force by the bolt and nut works with the same sharing ratio as the initial tightening as axial force fluctuation not only at the time of initial tightening but also against external load such as vibration where external force is applied to the screw fastening portion. .
  • Nf ⁇ ⁇ r b C
  • Nf The number of cycles of load until fatigue failure
  • ⁇ r Stress amplitude of load
  • b Stress index (generally 3 to 5)
  • C Material constant
  • the number of screw threads of the nut is generally selected, and the number of effective threads is selected to be the same in each aspect of the present invention.
  • the same tightening force and nut strength at the time of tightening are all adopted.
  • the same conditions apply to the nuts having eight threads and nine threads, which are compared with those of the conventional system 7, except for the number of threads.
  • the present invention mode (C) the analysis in the case of 7 threads and the analysis with 8 threads are performed, and the load sharing of the conventional method 7 and 8 is compared respectively.
  • Fig. 4-1 in the conventional method, the internal stress is highest at the first meshing thread (marked by 1 in Fig. 4-1 (a)), and the second ridge (marked by 2 in Fig. 4-1). In the third peak (marked 3 in Fig. 4-1), the stress drops sharply.
  • Fig. 4-4 (a) as the load sharing ratio of all threads
  • Fig. 4-4 (b) shows a comparison of the load sharing ratio in a bar graph.
  • the bar graph of the white frame display For the conclusion of the conventional method 7 mountain, it is shown by the bar graph of the white frame display.
  • FIG. 4-1 It is a longitudinal cross-sectional view which shows an example of the nut of the 1st aspect (A) of this invention.
  • A Cross-sectional view of nut
  • Example of aspect (A) of this invention and the conventional system nut The load share ratio comparison of FIG. 4-1.
  • the longitudinal cross-sectional view which shows an example of the nut of the 3rd aspect (C) of this invention.
  • the numerical comparison table of the load share rate of an example of the nut of the 3rd mode (C) of the present invention and a conventional system.
  • the nut of the present invention is A.
  • a convex-shaped space is concentrically formed on the bearing surface on the nut fastening side around the axis of the screw, and the space is connected by a straight line, a curve or a combination thereof.
  • a space is formed as a shape, the depth from the bearing surface of the space is L 2 , and the axial length from the valley bottom of the first screw of the fully threaded portion of the nut to the bearing surface is L 1 When forming the space, when the depth L 2 of the space is L 1 ⁇ L 2 ⁇ L 1 + length of thread 5 pitches; B.
  • the recess has an inner wall and a curve, straight line, or the like rising perpendicularly from the nut bearing surface
  • a nut having a two-part structure comprising a nut body having a screw shaft portion provided with a screw thread inside and a flange bearing surface portion and a pipe-like nut component having a chamfered bearing surface on at least one end face inner diameter side
  • a shape of a longitudinal sectional view of the nut body is T-shaped, and a length in which a screw shaft portion of the nut body is introduced from the flange seat surface portion of the nut body toward the inner object of the nut component is The hollow pipe-like nut component on the outer surface of the screw outer surface so that the incomplete screw thread length s + the length of the screw pitch 0.5 ridges or more and the length of the incomplete screw threads s + the screw pitch 5 ridges or less In which the bottom of the T-shaped nut body is not in contact with the object, and the top of the nut part is in contact with the f
  • the meshing first peak By forming; By increasing the load sharing after the third peak by making the flow of the force of the load received by the nut more directed to the open side meshing thread with low load sharing, the meshing first peak
  • the present invention is characterized in that it is configured to reduce the maximum load sharing of and reduce the load concentration on the meshing first peak.
  • the nut of the first aspect (A) and the second aspect (B) of the present invention is a one-piece structure, and a convex space is formed toward the open side on the bearing surface of the central portion on the fastening side of the nut
  • the process of forming the concave portion is performed, and the “flow of force” is made to pass through the nut bearing surface and the outer peripheral portion of the nut body, and to be directed to the third and subsequent open side of the screw.
  • the third aspect (C) is a two-part configuration of a nut body and a nut part, in which “flow of force” is directed to the open side of the screw on the third and subsequent sides of the screw using the nut body and the nut part It is. With such a structure, it is possible to provide a nut characterized by having a structure capable of simultaneously reducing the load sharing of both the initial tightening load and the external force load applied to the meshing first peak thread.
  • the screw thread conforms to JIS B 0205 (ISO 724).
  • the length is based on one pitch of a screw, but there are a plurality of bolts and nuts having the same thickness but different in thread pitch, so in this case the thread thickness is not used.
  • the screw pitch is adopted as one reference of the length.
  • the structure of the first aspect (A) is taken up as a representative, and the reduction of the load on the first engagement mesh is described.
  • the first aspect (A) in the shape of a longitudinal cross-sectional view of a nut, a space of an upwardly convex shape connected to a bearing surface on a nut fastening side by a curve, a straight line, or a combination thereof centered on the screw axis.
  • the thickness of the screw shaft portion of the nut having a screw thread inside is not constant because of the structure between the space and the nut screw thread, and the shaft portion thickness connected from P 2 side to P 1 side is P 2 It is also possible to make a gradual change from P 1 to P 1 , and the P 2 side can be made thicker and the P 1 side of the seat surface can be made thinner by a curve, a straight line, or a combination of them.
  • FIG. 1 is a longitudinal sectional view of the nut (a), a plan view (b) seen from the open side of the nut, and a plan view (c) seen from the seat surface
  • 1 being a nut
  • 2 being a bolt
  • 3 being a fastening 4 is a space between the nut bearing surface and the lowermost end of the nut shaft
  • 5 is a convex space above the nut bearing surface
  • 7 is the screw shaft lowermost end
  • 8 is a nut fastening side
  • 9 is a release of the nut
  • the side 9a is a nut open end
  • 14 is a nut bearing surface
  • 17 is an outer peripheral portion of the nut
  • 18 is a screw shaft portion provided with a screw thread inside
  • 19 is a nut screw thread.
  • the force proceeds along the inside of the nut to the curve inside on the outer periphery of the space 5, then enter the bolt through the deepest (P 2 near) the street each thread space 5.
  • P 2 threads 19 nearest from the vicinity in the example of FIG. 1 is the third nut thread.
  • the other forces are transmitted to the fourth, fifth, sixth and seventh.
  • the force toward the open side is transmitted to the other bolt thread, and a large amount of internal stress is applied to the third and subsequent threads.
  • the bolt remains engaged by the axial force and the 1st peak receives the maximum principal stress (tensile stress), but the load sharing of the 1st peak decreases relatively by receiving a lot of force on the open side of the nut .
  • the load on the first meshing engagement between the bolt and the nut is significantly reduced as compared with the structure of the conventional system.
  • FIG. 1 is a view for explaining the relationship of the depth of the space 5 in the first aspect (A) of the present invention, wherein P 1 is the bottom of the first full thread in the screw shank 18 of the nut. located in central, P 2 is located at the deepest portion in the depth direction of the space. Let L 1 and L 2 be distances from the bearing surface 14 of the nut to P 1 and P 2 , respectively.
  • FIG. 1 shows an arbitrary cross section within one thread pitch through the central axis of the nut and as shown in the enlarged view of the nut screw shank 18, the screw inlet at the position of the lowermost part 7 of the screw shank 18.
  • the distance L 1 from the seat surface 14 of the P 1 is the sum over distance dimensions and thread chamfer length and incomplete thread portion length of the gap 4.
  • the point P 1 and the space 5 in the thread root center of the first thread of the seating surface side of the nut thread that is a complete thread portion deepest relationship P 2 in the part is at a distance L 1 and L 2 from the seating surface, to set the dimensions of the L 2> L 1 and becomes L 2.
  • L 1 is one pitch distance when the rotation of 360 degrees because of the screw is changed, L 2 is often a constant numerical by molding.
  • L 2 is preferably at least deeper than L 1 , but the upper limit of depth is suitably L 1 + length of 5 pitches of screw threads.
  • the basic form 1 it is set to P 2 to the position of a length of about 2.4 pitch than P 1.
  • changing the thickness of the screw shaft 18 toward the fastening side or changing the shape from the deepest portion (P 2 ) of the space 5 to the shaft is the same. It is also possible to form in the vicinity of the lowermost portion 7 by the thickness. It is preferable that the shape be integrated with the shape of the space 5 and that a shape of a straight line, a curved line, or a combination thereof be adopted. It is preferable to provide a curve near the lowermost portion 7 to avoid stress concentration.
  • the space 5 having the convex shape is practically used as the space 5 having a shape connected by a smooth curve or a straight line as shown in an example or a modification of the basic form Structure.
  • the upward convex shape may be any shape without departing from the object of the aspect (A) of the present invention, and is included in the invention of the first aspect (A).
  • FIGS. 1-5 (a) and (b) show two modifications to FIG. 1, but mainly the shape of the space 5 and the outer shape in the seat portion are different. In either case, the force entering from the object 3 is passed through the inside of the nut 1 and directed to the open side of the three or more threads engaged with the mating bolt. Shapes having similar effects can be determined according to various conditions such as manufacturing requirements, in addition to the modification shown in FIGS.
  • What is important in the present embodiment (A) is the formation of an upwardly convex space 5 formed on the bearing surface side of the nut.
  • L 2 is set such that L 1 ⁇ L 2 ⁇ L 1 + length of 5 pitches of screw thread is satisfied, and the force passing near P 2 and the force pulled from the bolt
  • the von Mises equivalent stress distribution diagram of Fig. 1-1 corresponding to the aspect (A), the vector diagram of the maximum principal stress (tensile stress) where the flow of force can be seen in Fig. 1-2,
  • the flow of force can be confirmed by the vector diagram of the minimum principal stress (compression stress) in Fig. 1-3.
  • small arrows are closely arranged, the direction shows the direction of force, the length shows the magnitude of force, and the density of the arrangement is the situation where a lot of force flows in each direction at that place Is shown.
  • the von Mises equivalent stress distribution diagram of FIG. 1-1 visualizes the above vector diagram as an overall stress distribution, and is color-coded in black and white four gradations. Focusing on where the direction of the arrow points in the vector diagrams (Fig. 1-2, Fig. 1-3), the points where many forces are facing go to the threads in the nut, but where many are pointing It is No. 3 and No. 4 of the nut thread. It can also be seen that there are also many toward the open side 5, 6 and 7 thread. As for the nut screw thread fastening side, it is transmitted while bending in the direction of No. 2 and then No. 1 so as to wind a vortex from the vicinity of P 2 . In Fig.
  • the bolt thread and the bolt shaft are subjected to an axial force that pulls them toward the fastening side, so from the diagonal thread surface of the nut to the diagonal thread surface of the bolt I can see how I was concentrating and putting power. Since the bolt axial force is directed to the fastening side, the No. 1 thread is subjected to the largest tensile stress, but No. 1 and No. 2 of the nut are bent from around P 2 around the screw shaft 18 It receives more of the small force and the tensile force from the bolt, and it is in a situation where it is pulled to the fastening side in order of strength, such as the nut screws No. 3, No. 2 and No. 1. For this reason, in the case of the No. 1 nut screw, a black color appears to indicate that the internal stress is low. The shape effect of the screw shaft is added here.
  • the force from the nut flows in the direction of the thread ridge after the third peak, and the fastening meshing first peak Reduce the load on The load sharing after the third peak has increased compared to the conventional method, and the power reaches to the seventh peak.
  • the stress large area (white display area) in Fig. 1-1 is narrow and small for the 1st, 2nd, and 3rd thread threads, and dark gray (stress is slightly small for 4th, 5th, 6th and 7th).
  • the vector diagram 4-2 of the maximum principal stress, and the figure 4-3 in the minimum principal stress, in the conventional manner the situation where it is controlled by the force passing through the innermost diameter side of the nut
  • the stress distribution map of FIG. 1-1 of the present invention has a completely different stress distribution, and the aspect (A) of the present invention is such that the flow direction of force is tightened toward the third mesh and thereafter. It is clearly shown to reduce the load on the mesh 1st peak.
  • the load sharing ratio of the meshing first peak in one example of the aspect (A) is 26.3% (conventional method: 35.6%).
  • a comparison chart of this result with that of the conventional method 7 mountain based on the load sharing ratio of each mountain is shown in FIG. 1-4 (a), and a comparison bar graph of this numerical value is shown in FIG. 1-4 (b). From this comparison, it can be read that the load sharing after the third peak is increased and the load sharing of the meshing first peak is reduced in the example of the nut of the mode (A) as compared with the conventional method.
  • each corner of the convex space structure nut in the first aspect (A) the processing of each corner is preferably as follows. It is preferred to use corner shapes which are made with optimal stress concentration relaxation curves for each part location.
  • the stress concentration relaxation curve has, for example, a quadratic curve (simple R, composite R, ellipse, etc.), and a straight line such as an oblique C-cut can also be used.
  • the screw surface conforms to the JIS standard, and the sliding surface has a fine-class finish, and the other surface has an intermediate-class finish or a required surface roughness.
  • the surface roughness be consistent with the surface treatment described later.
  • the nut (B) of the present invention has a rectangular recess on the screw center side of the bearing surface on the fastening member side of the nut in the shape of the longitudinal sectional view of the nut, and the recess rises vertically from the bearing surface It has an inner length and a curve, a straight line, or a corner and an upper surface that combines them, and the axial length from the position of the upper surface is the axial length of the incomplete thread of the nut plus the two pitch lengths of the nut
  • Lb is at least 0.001 times La
  • a recess having a length of 1 time or less and Lh of 0.5 to 5 times the length of La is formed concentrically with the center of the screw.
  • the flow of force entering the nut upon fastening enters from the entire surface of the nut bearing surface in contact with the object, and flows along the wall of the nut recess, It passes near the corner, goes to the vicinity of the central part of the nut, after the third mountain on the open side, and flows widely dispersed in all the screw threads.
  • the tensile stress that enters the nut from the bolt is the largest at the first mesh, the stress applied to the screw thread of the nut during fastening can be shared more by the screw thread side at the open end, It is possible to reduce the load on the first engagement between the nut and the bolt.
  • FIG. 2 is a longitudinal sectional view showing an example of the nut of the second aspect (B) of the present invention, and the nut 1 has a structure having a recess 10 in the lower portion of the inner diameter of the nut.
  • a wall 11 standing vertically from a nut bearing surface 14 in contact with the object 3 to be fastened, and a corner portion 12 having a straight line sandwiched by curves connected thereon (a straight line on this corner 12 is from the fastening side of the nut It is preferable to face the screw valley bottom of the second and subsequent peaks.
  • the recess 10 has an axial length La, which is the sum of the chamfered dimension of the threaded portion of the nut 1 + the axial length s of the incompletely threaded portion and the two pitches of the nut.
  • Lb is 0.001 times or more of La as Lb is the axial length from Lb to the upper surface 13 and Lh is the radial length of the recess 10 from the thread valley bottom 15 of the nut 1 to the inner wall 11 of the recess 10
  • the recess 10 is formed concentrically with the center of the screw, with a length not more than double and Lh being a length not less than 0.5 times and not more than 5 times La.
  • Fig. 2-1 shows a first modification, in which the corner portion 12 of the recess 10 has one stress concentration relaxation curve structure, and the corner portion 12 is connected to the upper surface 13 so as to sequentially chamfer and incompletely screw , Through the thread root 15 to the thread 19.
  • the dimension in the recess is such that the axial length of the incomplete thread portion of the nut 1 + the axial length s of the chamfer plus the length of 2 pitches of the nut is La, and from the bearing surface 14 to the upper surface 13 of the recess 10 Lb is 0.001 times or more and 1 times or less of La when the axial length of L is Lb, and the radial length of the recess 10 to the thread valley bottom 15 of the nut 1 and the inner wall 11 of the recess 10 is Lh.
  • the recess 10 is formed concentrically with the center of the screw with a length Lh of 0.5 to 5 times the length of La. In the modification of FIG. 2-1, Lh is about 1.1 times La.
  • the force flow can be made to flow much from the nut bearing surface 14 through the outer peripheral portion of the nut and to the third and subsequent peaks on the open side.
  • the nut has a simple shape for processing, and has the advantage of easy manufacture including shape confirmation.
  • FIG. 2 A Mises equivalent stress distribution chart of one example of FIG. 2 which is a basic example of the present mode (B) is shown in FIG.
  • the force entering from the nut bearing surface 14 often flows toward the 45 ° diagonal thread in the nut bearing surface. From the point close to the center of the bearing surface 14 toward the screw thread side 45 degrees diagonally parallel to the corner 12 straight line part, the force flowing from the nut thread No. 3 to No. 4 and 45 degrees from the stepped outer periphery of the nut It is seen that the screw heads 5 and 6 head to the screw thread side while leaning to the screw thread side.
  • the force flowing around the corner 12 and flowing horizontally to the first mountain on the fastening side parallel to the upper surface 13 is small.
  • Such a black portion is not found in the conventional nut (FIG. 4-1), and it is considered that the force passing through the corner 12 is flowing on the slightly open side of the black portion.
  • the force spread in the nut will receive the force drawn from the bolt thread when it reaches the thread, but the load on the first meshing tooth as a result of the force being distributed to many threads is conventionally Compared to the scheme is reduced.
  • the ability to direct the force entering from the nut bearing surface 14 to the open side of the nut can be easily controlled as compared with the modification of FIG.
  • the length of the upper surface of the reference numeral 13 in the figure is increased, and the Lh length in the bearing surface is increased to about 2.0 times La, or the inclination of the straight portion of the corner 12 is inclined by more than 45 degrees.
  • the direction of the force can be controlled by optimally combining the elements of the recess, and the load sharing to the meshing first peak can be reduced.
  • the load sharing ratio of the meshing first peak shows a numerical value less than 30%.
  • FIG. 2-3 A bar graph comparing the load sharing rates of the example of FIG. 2 of the mode (B) and the conventional method is shown in FIG. 2-3 (a) and FIG.
  • the black frame display in the bar graph shows a modification of the aspect (B).
  • the load sharing ratio is reduced to 29.6% in the modification of the mode (B) as compared with 35.6% in the conventional method in the meshing first peak.
  • the aspect (B) increases after the third peak.
  • the shape of the open side of the nut of the present embodiment (B) may be a shape that can use a conventional fastening tool, such as a hexagon or a square.
  • the screw has a fine-class finish according to JIS standard
  • the nut seat surface has a fine-class finish
  • the other surface has a rough finish
  • it is preferred to have a co-finish it is more preferred to have a surface that is compatible with the surface treatment.
  • the nut bearing surface 14 and other surfaces all corners preferably have a shape having a stress concentration relaxation curve such as a circular arc, a quadratic curve such as a part of an ellipse, etc. Is desirable.
  • a nut having a two-part structure comprising a nut body having a screw shaft portion provided with a screw thread inside and a flange bearing surface portion and a pipe-like nut component having a chamfered bearing surface on at least one end face inner diameter side
  • a shape of a longitudinal sectional view of the nut body is T-shaped, and a length in which a screw shaft portion of the nut body is introduced from the flange seat surface portion of the nut body toward the inner object of the nut component is
  • the hollow pipe-shaped nut component is formed on the outer surface of the screw outer surface so that the incomplete screw part length s + the length of the screw pitch 0.5 or more, and the length of the incomplete screw part s + the screw pitch 5 m or less
  • the T-shaped nut body is disposed so that the lowermost portion of the T-shaped nut body is not in contact with the object, and the uppermost portion of the nut part is in contact with the flange-like
  • a longitudinal sectional view of a nut according to a third aspect (C) of the present invention is exemplarily shown in FIG.
  • the shape of the longitudinal sectional view of the nut body 1 is substantially T-shaped, and the nut body 1 is integrated with the screw shaft portion provided with a screw thread inside, and at least on the side surface of the flange lower surface portion screw shaft portion 18 of the nut body 1 It has a structure in which a pipe-shaped nut part 6 having a chamfering structure for preventing interference with the shaft part 18 is disposed on one inner diameter side of one side, and the nut main body shaft part 18 is rotatable in the nut part 6
  • the body 1 is screwed with a bolt 2 inside, and contacts and rotates with the nut part 6 at the sliding surface 16.
  • the length from the top surface 22 of the nut part 6 to the bearing surface 14 is from the flange seating surface of the nut body 1 to the top of the screw shaft so that the screw shaft lowermost part 7 of the nut body 1 does not contact the object 3 to be fastened.
  • the structure in which the nut part 6 is in contact with the object 3 is shown longer than the length to the lower part 7.
  • the upper open side outer shape of the nut body 1 can be shaped according to the fastening tool.
  • the thickness of the screw shaft portion 18 in which a screw thread is provided in the axial direction of the nut main body 1 may be constant, or the open side is thick and the object side is narrowed, and further, the length of the shaft portion is halfway It can also be made thinner.
  • the bearing surface 20 of the nut part 6 can be enlarged to reduce the contact pressure at the time of fastening of the nut part 6 and the object 3 to be fastened.
  • the fastening side lowermost surface 7 of the nut body 1 is not in direct contact with the to-be-fastened Since it is in contact with the object 3, the flow of force at the time of fastening is directed to the open side of the nut body 1 via the contact surface 16 between the nut component 6 and the nut body 1 and further directed to each thread. At this time, the force enters the nut body 1 from the nut part 6, but the position thereof is much from the vicinity of the innermost diameter portion of the contact surface 16 where the nut part 6 and the nut body 1 are in contact. Go to the second and subsequent threads and reach the open thread while expanding.
  • the curved portion transitioning from the flange portion of the nut body to the screw shaft portion 18 and the inner diameter side shoulder portion of the nut part 6 desirably have each other even if their shape and size may change.
  • a stress concentration relaxation curve capable of maintaining a non-interfering structure is provided to prevent stress concentration on both the nut body and the nut component.
  • the load sharing situation of the thread changes from the relative relationship of the position of the thread at the axial height of the screw in the screw shank 18 which corresponds to the contact face 16 of the nut part 6 and the nut body 1.
  • L 1 indicates the distance from the point P 1 at the bottom of the fully threaded No. 1 screw valley on the screw thread side of the screw thread 18 of the nut to the nut bearing surface 14.
  • P 1 and the bearing surface of the nut there is a gap 4 and a total length s of the chamfer and the screw imperfection.
  • the number of screw threads of the nut is eight, as an example. This is due to the purpose of improving the rigidity of the nut itself due to the balance of force due to the flow of a large amount of stress on the open side of the nut due to the influence of the screw shaft. As an example, a step or a taper or a combination of these is provided on the outer periphery of the screw shaft portion 18 of the nut body 1. Moreover, in FIG. 3, it is the structure which increased the contact area which the bearing surface 20 of the nut component 6 contacts the to-be-fastened object 3, and the effect of reducing the fastening surface pressure of the bearing surface 20 which the nut component 6 and the to-be-fastened object 3 contact is there.
  • the nut body 1 and the to-be-fastened object 3 make contact at the surface 16 of the flange bearing surface of the nut body 1.
  • the bolt 2 is directed in the direction in which the screw thread comes out from the side of the object to be fastened, and is set to be screwed with the nut body 1.
  • a large amount of force can be flowed after the third thread on the open side thread of the nut main body, and the load reduction in the first mesh can be implemented.
  • Such usage and chamfering shapes are also part of the present invention.
  • the advantages in this case include, in addition to the effects of the aspect (C), reduction in the number of parts, weight reduction, reduction in the amount of projection of the nut, and the like.
  • a nut body having a structure with eight threads is used for FEM analysis of the aspect (C) nut. This is because the rigidity of the nut itself is improved by the flow of a large amount of stress on the open side of the nut under the influence of the screw shaft. According to this, the conventional nut of the comparison standard uses the value of the thread 8 thread.
  • the force entered from the bearing surface 20 of the nut part 6 is black at the lowermost part, and obliquely upward from dark gray to light gray toward the nut main body 1, the nut main body 1 and nut
  • the surface 16 with which the component 6 contacts is white with high compressive stress at the top and bottom, which is the maximum stress, but in this part, the 7 to 8 thread ridges of the nut main body 1 have a white or gray band of high stress facing You can see what you are doing.
  • white and light gray are seen toward the nut shaft portion 18, but this portion is under tensile stress. A white color is visible through this portion to the bottom of the thread between nut threads # 4 and # 3 and # 3 and # 2.
  • FIG. 3-1 of this embodiment (C) A comparison of FIG. 3-1 of this embodiment (C) with FIG. 4-1 by the conventional method reveals that the von Mises equivalent stress distribution map has a completely different appearance.
  • Fig. 4-1 of the conventional method the force is immediately applied to the fastening side No. 1 and most of the forces are transferred by No. 1 and then gradually become smaller as the second and third. It can be seen that they are only sharing.
  • FIG. 3 Comparison of an example of the aspect (C) and the conventional method is shown in FIG. 3 (a) a load sharing ratio, and (b) a bar graph, for performance comparison of the aspect (C) of the present invention and the conventional method.
  • the load sharing ratio of the meshing first peak of this mode (C) is 22.9%, which is far from 34.5% of the conventional system.
  • the load carrying rate in the mode (C) is higher. This comparison is made with both nut threads of eight.
  • the analysis of the modification in the 7th mountain of the aspect (C) of the present invention is shown in the stress distribution map of Miess in FIG. 3-3, and the comparison with the 7th mountain of the conventional method is shown in FIG. Comparative bar graphs are shown in -4 (b).
  • the load sharing ratio of the meshing first peak in this modified example is 24.0%, which is significantly different from 35.6% of the conventional system.
  • both are compared with seven threads.
  • the aspect (C) is found to be correlated between the axial position of the flange bearing surface of the nut body 1 and the position of the screw thread of the nut body (screw shaft portion projection amount), and the amount of force flow to the open side It is suggested that it affects the load sharing of the mesh 1st mountain.
  • the protrusion amount of the nut body shaft 18 is changed, and Fig. 3-1 is different from about 3.5 mountain in Fig. 3-3 and Fig. 3-3 is about 4.3 mountain. There is.
  • the corners of the parts of the third aspect (C) of the present invention (C) and other parts in contact with the corners 20 and the nut body of the nut part 6 are stress concentration relieved It is desirable to provide a curve. Also, the size and shape of these stress concentration relaxation curves can be determined arbitrarily.
  • the surface roughness of the bearing surface 20 of the nut part 6 is fine-finishing, or both the surface 16 where the nut body 1 and the nut part 6 contact are fine-finishing, the surface of the screw is a surface roughness according to JIS, other surface roughness In order to have consistency with the surface treatment to be described later, such as rough finish or co-finishing, it is preferable to set an optimal surface roughness depending on the place.
  • the T-shaped nut structure does not necessarily have to be a strict T-shaped structure, and may have a modified structure without departing from the scope of the invention.
  • it may be a cross structure.
  • the nut body upper part it is also possible for the nut body upper part to have a shape that can use a fastening tool such as a normal hexagon, which is more preferable.
  • the flow of the load force received by the nut as described above is achieved by the open side meshing thread with low load sharing.
  • the load sharing after the third peak as a nut structure that is directed more, it is possible to provide a nut configured to reduce the maximum load sharing of the meshing first peak.
  • the nuts according to the first to third aspects of the present invention can utilize materials conventionally used.
  • materials alloy steels such as mild steel, carbon steel, nickel chromium steel, chromium steel, nickel chromium molybdenum steel, non-ferrous metals such as stainless alloy steel, aluminum alloy, nickel alloy, titanium alloy, resin, ceramic (oxide, nitrided Materials, materials such as objects, carbides, etc. are suitably used.
  • the screw can be formed by the same method as the conventional method, for example, screw forming with a tap, NC (numerical control) lathe, machining center (MC), combined processing machine (combined processing machine of lathe and milling cutter), EDM, or any combination thereof, press plastic working, cold / hot / warm press, forging, casting, injection molding, precision casting, 3D printer processing, molding, MIMS, or for roughing material production It can do by combining them.
  • NC numbererical control
  • MC machining center
  • combined processing machine combined processing machine of lathe and milling cutter
  • the formation of the nut of the first aspect (A) by an NC lathe will be described as an example.
  • the external part is manufactured by cold, warm, hot forging / pressing, cutting, nut former, Swiss type automatic lathe, etc.
  • the space part on the seat side of the nut or concave rectangular rectangular shape is NC lathe, automatic disc, Etc.
  • the nut of the present invention is manufactured by forming a screw thread of a nut using cutting, grinding, cutting tap, and rolling tap in the same manner as forming a conventional screw thread. be able to.
  • a space or a substantially rectangular recess may be formed on the bearing surface side of the nut, and then the outer peripheral shape may be formed.
  • a member can be divided roughly into a member which becomes a nut body and a member which becomes a nut part.
  • the outer shape of the nut and the preparation of the screw lower hole adopt hot press / cold / warm press, forging, cutting, casting, etc., and produce a one-part type nut or a substantially T-shaped shape.
  • the top is formed so that a fastening tool such as a hexagon can be used to facilitate fastening with a normal tool, and a tap is passed through a pilot hole made by cutting, cold / hot forging, casting, etc. Form a mountain / valley.
  • the threaded portion may be formed by turning or grinding.
  • the nut part can be manufactured by cutting a pipe, cold / warm / hot forging, casting, continuous automatic cutting from a round bar with a CNC lathe, etc., or a combination of these. It may be formed by a 3D printer. When it is made of resin or ceramic, a combination of methods such as injection molding, sintering and the like, and cutting and grinding may be performed. The surface roughness of the contact surface of the nut and the nut part can be selected and adopted to reduce the sliding resistance. It can be processed by selecting or combining from a mirror polished surface, a polished surface, a precision cutting surface, a pressing surface with a precision die, micro shot peening, glass bead shot and the like. Also, in the combination of the nut body and the nut part, the nut body rotates while rotating around the screw central axis, so that the fastening object surface and the nut screw central axis are kept perpendicular. It is desirable to make
  • the coefficient of friction ⁇ is also dry ⁇ ⁇ 0.5, and wet ⁇ ⁇ 0 It is known to be .1.
  • the lubricant flows out, the oxide film on the metal surface peels off, and a metal surface appears.
  • a strong pressure contact state where metal bonding occurs on the metal surface is achieved.
  • S-DLC segment-like diamond-like carbon
  • a bolt side thread engaged with at least a bolt on the thread surface of the first thread or part or all of more threads.
  • the screw thread surface preferably includes at least a meshing first screw thread surface, and it is preferable that the DLC film is also formed on the more open side screw.
  • the DLC protective film By forming the DLC protective film, roughening and peeling of the metal surface can be suppressed, the coefficient of friction can be stabilized, and more stable fastening can be achieved.
  • the DLC film is in the form of segments which are divided, for example, in a grid by grooves (S-DLC film).
  • the nut body and the nut component Covering the sliding surface 16 or the surface 14 of the nut part in contact with the object to be fastened with a diamond-like carbon (DLC) film to form a protective film realizes smooth fastening operation and stable fastening.
  • DLC diamond-like carbon
  • the DLC film is in the shape of, for example, a grid divided into segments by a groove without a film (S-DLC film).
  • S-DLC film the groove portion without the film becomes an oil groove, and when the oil is supplied, the seat surface friction coefficient is stabilized, which contributes to the stability of fastening.
  • vapor deposition In order to deposit the DLC film on the surface on which the nut body and the nut component slide, the bearing surface of the nut, and the inner surface of the screw, vapor deposition (CVD or PVD) is preferred. Examples thereof include plasma CVD using a high frequency power as a power source or sputtering such as magnetron sputtering or ion beam sputtering.
  • the film thickness of the DLC film depends on the shape of the nut, the part of the nut, the usage, etc., but is usually 0.01 to 10 ⁇ m, and more preferably 0.5 to 3 ⁇ m.
  • BN film, WC film, CrN film, HfN film, VN film, TiN film, TiCN film, Al 2 O 3 film, ZnO film, SiO 2 film, alumite, metal plating, solid lubricating layer, manganese phosphate conversion treatment It is possible to select any of carburizing and quenching, nitriding, chromizing, polymer resin coating, or a combination thereof. These membranes are effective in realizing smooth fastening operation and stable fastening.
  • metal plating As types of surface film formation or surface treatment, metal plating, polymer resin coating, alumite treatment, vacuum deposition, ion plating, plasma treatment such as PVD, CVD and the like can be suitably applied.
  • surface treatment can be applied to the outer surface of the nut or nut part, and weather resistance improvement, appearance improvement, identification indication provision, decoration, etc. can be appropriately performed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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Abstract

La présente invention concerne un écrou dans lequel, en déplaçant la force de fixation dans la fixation boulon-écrou vers le côté ouvert de l'écrou et en augmentant le partage de charge parmi les filets à partir du troisième filet, il est possible de réduire la charge sur le premier filet en prise, qui porte la charge maximale, et d'étendre la résistance à la fatigue du boulon par rapport à la fracturation d'axe de fissure. Un premier mode de réalisation de l'écrou est conçu de telle sorte que, en ce qui concerne la forme de l'écrou dans une vue en coupe longitudinale, un espace ayant une forme convexe sur la partie supérieure est formé de manière concentrique, centré sur l'axe de filetage, sur la face d'écrou côté fixation. L'espace convexe est une structure dans laquelle un espace convexe est formé sous la forme d'une forme raccordée par des lignes droites, des lignes incurvées ou une combinaison des deux. En formant ledit espace de telle sorte que, lorsque L2 est la profondeur de l'espace convexe à partir de la face d'écrou et L1 est la longueur dans la direction axiale de l'écrou du premier fond d'une partie filet complet à la face de l'écrou, ladite profondeur d'espace convexe L2 est dans la plage de L1 < L2 ≤ L1 + 5 longueurs du pas de vis, davantage de contrainte sur les filets de l'écrou pendant la fixation est déplacé vers le troisième filet vers le côté ouvert de l'écrou et la concentration de la charge sur le premier filet mis en prise de l'écrou et du boulon est réduite.
PCT/JP2018/047682 2017-12-25 2018-12-25 Écrou de fixation WO2019131685A1 (fr)

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JPS465709Y1 (fr) * 1967-03-17 1971-03-01
JPS57177922A (en) * 1981-04-24 1982-11-01 Toshiba Corp Bolt
JPS5945320U (ja) * 1982-09-20 1984-03-26 新日本製鐵株式会社 締結用ナツト
JPS59166010U (ja) * 1983-04-22 1984-11-07 新日本製鐵株式会社 ナツト
JPS61136013A (ja) * 1984-12-06 1986-06-23 株式会社　佐賀鉄工所 座金の共回り防止構造
US5927921A (en) * 1997-11-11 1999-07-27 Sps Technologies, Inc. Enhanced fatigue nut
JP2003004016A (ja) * 2001-06-22 2003-01-08 Sumitomo Metals (Kokura) Ltd 高力ボルト、ナット及び座金
JP2005282668A (ja) * 2004-03-29 2005-10-13 Rikogaku Shinkokai 硬質被膜で締結摺動面を被覆した締結治具部材、締結治具部材を装着した締結物体及び締結治具部材の製造方法
JP2010209714A (ja) * 2009-03-09 2010-09-24 Nissan Motor Co Ltd 内燃機関の複リンク式ピストンクランク機構

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JPH01303308A (ja) * 1988-05-31 1989-12-07 Tsukiboshi Seisakusho:Kk ロックナット
JP4344927B2 (ja) * 2003-12-24 2009-10-14 住友金属工業株式会社 締結用部材、車輪とブレーキディスクとの締結方法及び鉄道車両用ディスク付き車輪
US9708912B2 (en) * 2014-10-30 2017-07-18 Siemens Energy, Inc. Turbine rotor nut and bolt arrangement with improved fatigue resistance under centrifugal load

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS465709Y1 (fr) * 1967-03-17 1971-03-01
JPS57177922A (en) * 1981-04-24 1982-11-01 Toshiba Corp Bolt
JPS5945320U (ja) * 1982-09-20 1984-03-26 新日本製鐵株式会社 締結用ナツト
JPS59166010U (ja) * 1983-04-22 1984-11-07 新日本製鐵株式会社 ナツト
JPS61136013A (ja) * 1984-12-06 1986-06-23 株式会社　佐賀鉄工所 座金の共回り防止構造
US5927921A (en) * 1997-11-11 1999-07-27 Sps Technologies, Inc. Enhanced fatigue nut
JP2003004016A (ja) * 2001-06-22 2003-01-08 Sumitomo Metals (Kokura) Ltd 高力ボルト、ナット及び座金
JP2005282668A (ja) * 2004-03-29 2005-10-13 Rikogaku Shinkokai 硬質被膜で締結摺動面を被覆した締結治具部材、締結治具部材を装着した締結物体及び締結治具部材の製造方法
JP2010209714A (ja) * 2009-03-09 2010-09-24 Nissan Motor Co Ltd 内燃機関の複リンク式ピストンクランク機構

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