WO2013094672A1 - 締結部材 - Google Patents

締結部材 Download PDF

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Publication number
WO2013094672A1
WO2013094672A1 PCT/JP2012/083027 JP2012083027W WO2013094672A1 WO 2013094672 A1 WO2013094672 A1 WO 2013094672A1 JP 2012083027 W JP2012083027 W JP 2012083027W WO 2013094672 A1 WO2013094672 A1 WO 2013094672A1
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WO
WIPO (PCT)
Prior art keywords
bolt
tapered cylindrical
fastened
cylindrical portion
tapered
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2012/083027
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English (en)
French (fr)
Japanese (ja)
Inventor
忠承 山▲崎▼
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Yamazaki active KK
Original Assignee
Yamazaki active KK
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.)
Filing date
Publication date
Application filed by Yamazaki active KK filed Critical Yamazaki active KK
Priority to EP12860487.3A priority Critical patent/EP2796734B1/en
Priority to US14/367,834 priority patent/US9212682B2/en
Priority to JP2013550323A priority patent/JP5787197B2/ja
Priority to KR1020147019735A priority patent/KR101985316B1/ko
Publication of WO2013094672A1 publication Critical patent/WO2013094672A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16B33/00—Features common to bolt and nut
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23K—SOLDERING OR UNSOLDERING; WELDING; CLADDING OR PLATING BY SOLDERING OR WELDING; CUTTING BY APPLYING HEAT LOCALLY, e.g. FLAME CUTTING; WORKING BY LASER BEAM
    • B23K20/00—Non-electric welding by applying impact or other pressure, with or without the application of heat, e.g. cladding or plating
    • B23K20/12—Non-electric welding by applying impact or other pressure, with or without the application of heat, e.g. cladding or plating the heat being generated by friction; Friction welding
    • B23K20/129—Non-electric welding by applying impact or other pressure, with or without the application of heat, e.g. cladding or plating the heat being generated by friction; Friction welding specially adapted for particular articles or workpieces
    • 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
    • F16B35/00—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws
    • F16B35/04—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws with specially-shaped head or shaft in order to fix the bolt on or in an object
    • F16B35/06—Specially-shaped heads
    • 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
    • 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
    • F16B39/24—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening by means of washers, spring washers, or resilient plates that lock against the object
    • 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
    • F16B39/284—Locking by means of elastic deformation
    • 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
    • F16B5/00—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them
    • F16B5/02—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them by means of fastening members using screw-thread
    • F16B5/0241—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them by means of fastening members using screw-thread with the possibility for the connection to absorb deformation, e.g. thermal or vibrational

Definitions

  • the technical field of the present invention is to provide a locking bolt including a tapered cylindrical portion provided as a seating surface that is provided so as to gradually expand in diameter concentrically with the bolt shaft from the head of the bolt. And a taper cylindrical portion provided so that the diameter of the bolt gradually increases concentrically with the bolt shaft to which the nut is screwed from the head of the nut, and the end surface is provided as a seating surface in contact with the fastened body
  • the present invention relates to a locking member including a nut and a washer.
  • Fastening members such as bolts and nuts are widely used in various fields as means for fastening and fixing fastened bodies such as members and parts.
  • a fastening member having the following configuration has been proposed.
  • a fastening member that fastens a body to be fastened by a screw action, and a head portion for rotating the fastening member around an axis, and a head that is integrated with the head portion and concentric with the head portion from the base portion of the head portion
  • the extending end side is formed in a cylindrical shape whose diameter is gradually increased so as to be larger in diameter than the portion, and the extending end surface is provided with a tapered portion formed on a seat surface in contact with the fastened body, and the tapered portion Is formed in a conical curved surface, and the outer surface of the tapered portion is formed in a concave curved surface (see Patent Document 1). According to this, a to-be-fastened body can be reliably fixed by absorbing intense vibrations and impacts, and a loosening prevention effect can be obtained.
  • bolts and nuts (hereinafter referred to as “bolts and the like”) fastening members (including washers) share the same technical idea of loosening prevention, and are referred to as tapered portions (tapered cylindrical portions). It has a common configuration. About the taper cylindrical part of a nut, since it can be manufactured with an exclusive apparatus (parts oma), it has the form which can be mass-produced appropriately and cheaply. On the other hand, the taper cylindrical part of the bolt is formed by cutting, which increases the cost and cannot cope with mass production.
  • the outer peripheral surface is entirely a concave curved surface, so that the strength of the peripheral portion cannot be ensured properly and the outer dimensions are appropriate. Cannot be made smaller. Furthermore, if the ring width of the ring-shaped part formed by the seating surface that comes into contact with the body to be fastened is not only sufficient contact frictional resistance with the body to be fastened, but also tightening force such as bolts There is a risk that plastic deformation may occur by surpassing the elastic force of the tapered cylindrical portion due to impact and vibration caused by the body.
  • the problem to be solved regarding the fastening member such as the loosening bolt is that, firstly, a form that appropriately secures the strength of the peripheral part of the tapered cylindrical part and appropriately reduces the outer dimension has not been proposed. Secondly, no form has been proposed that can absorb the tightening force of bolts and the impact / vibration caused by the fastened body more appropriately without plastic deformation, and third, concentricity from the bolt head to the bolt axis. No reasonable manufacturing method has been proposed that can mass-produce a loosening bolt including a tapered cylindrical portion that gradually increases in diameter at an appropriate and low cost.
  • an object of the present invention is to provide a fastening member that firstly secures the strength of the peripheral edge of the tapered cylindrical portion and appropriately reduces the outer dimension, and secondly, tightening force such as bolts.
  • the present invention has the following configuration in order to achieve the above object.
  • the fastening member concerning this invention, it is a fastening member of the volt
  • the tapered tubular body is provided with a tapered tubular body portion that is formed in a tubular body that gradually increases in diameter toward a seating surface that is provided in the shape of a circular planar belt ring concentric with the shaft.
  • the taper angle of the portion is provided to be an acute angle, and the outer diameter of the circular planar belt ring-shaped seating surface is large in the range in which surface pressure is generated so that the seating surface is effectively pressed against the fastened body.
  • an upstanding surface that rises perpendicularly from the fastened body is provided on the outer peripheral surface of the tapered cylindrical portion.
  • an outer peripheral surface of the tapered cylindrical portion is formed by the rising surface and a concave curved surface continuous to the rising surface, and the wall of the tapered cylindrical portion is formed.
  • the thickness is equal to or gradually increased from the concave curved surface to the rising surface from the portion where the diameter expansion starts, and the thickness between the concave curved surface and the seating surface is the bolt tightening
  • the standing length of the standing surface can be set so as to secure a thickness to receive force and impact / vibration caused by the fastened body without plastic deformation.
  • the inner peripheral surface of the tapered cylindrical portion may be formed by a concave curved surface.
  • the bolt shaft is integrally provided from the head of the bolt so as to gradually increase in diameter concentrically with the bolt shaft, and the end surface is provided on the body to be fastened.
  • a locking bolt provided with a tapered cylindrical body portion provided as a seating surface in contact with a circular plane belt ring concentric with the shaft of the shaft, a shaft member constituting the axis of the bolt, a head of the bolt, and a tapered cylindrical body
  • a convex portion protruding in a short columnar shape is provided on the inner bottom portion of the head of the bolt surrounded by the tapered cylindrical portion so that the end surface becomes a joint surface of friction welding.
  • the surfaces joined by friction welding between the convex portion of the inner bottom portion of the bolt head and the shaft of the bolt are provided in the same shape. Can be characterized.
  • the tapered cylindrical body portion is provided so that the taper angle is an acute angle, and the outer diameter of the circular planar belt ring-shaped seating surface is the seating surface.
  • the tapered cylindrical body is provided with an upstanding surface that stands upright from the fastened body on the outer peripheral surface of the tapered tubular portion so that the surface pressure is generated in such a manner as to effectively contact the fastened body. It can be characterized by being.
  • an outer peripheral surface of the tapered cylindrical portion is formed by the rising surface and a concave curved surface continuous to the rising surface
  • the wall thickness is equal to or gradually increased from the head-side portion of the bolt that starts the diameter expansion to the portion that changes from the concave curved surface to the standing surface, and the thickness between the concave curved surface and the seat surface
  • the standing length of the upright surface is set so that the thickness can secure the thickness to receive the bolt tightening force and the impact and vibration caused by the fastened body without plastic deformation. it can.
  • the inner peripheral surface of the tapered cylindrical portion is formed by a concave curved surface.
  • the loosening prevention bolt according to the present invention, firstly, it is possible to provide a loosening prevention bolt that appropriately secures the strength of the peripheral edge portion of the tapered cylindrical portion and appropriately reduces the outer dimension, and secondly, the bolt It is possible to provide a locking bolt that can more appropriately absorb the tightening force and the impact and vibration caused by the body to be fastened without plastic deformation, and thirdly, a taper that gradually expands concentrically from the bolt head to the bolt axis. There is a particularly advantageous effect that the locking bolt including the cylindrical portion can be more rationally produced.
  • FIG. 17 is a side view of the locking nut of FIG. 16.
  • FIG. 17 is a plan view of the locking nut of FIG. 16. It is a bottom view of the locking nut of FIG. FIG. 17 is a cross-sectional view of the locking nut of FIG. 16 along AA. It is a perspective view of the locking nut of FIG. It is a front view which shows the other form example of the locking bolt of this invention. It is a side view of the locking bolt of FIG. It is sectional drawing of the locking bolt of FIG. It is a bottom view of the locking bolt of FIG. It is an analysis figure of the surface pressure concerning the seat surface of the locking bolt of the present invention. It is an analysis figure of the surface pressure concerning a seat surface of a locking bolt of a comparative example.
  • FIG. 27 is a front view of the locking washer of FIG. 26. It is a top view of the locking washer of FIG. It is a bottom view of the slack stopper washer of FIG.
  • FIG. 27 is a side view of the locking washer of FIG. 26.
  • FIG. 27 is a cross-sectional view of the locking washer of FIG. 26 taken along the line AA. It is a front view which shows the use condition of the other form example of the locking washer of this invention.
  • the loosening prevention bolt of this embodiment is provided so as to surround the bolt shaft 21 integrally from the bolt head 11 so as to gradually expand in diameter concentrically with the bolt shaft 21, and the end surface is fastened 40 (FIG. 14).
  • the outer peripheral surface 12b of the tapered cylindrical portion 12 is produced by a method for manufacturing a locking bolt in which a concave curved surface is provided.
  • the taper angle of the tapered cylindrical portion 12 according to the present invention is an acute angle ⁇ (see FIG. 31).
  • the bolt shaft and the circular plane belt ring-shaped seating surface are concentrically spaced apart from each other at a predetermined interval.
  • a bolt head 11 constituted by a shaft member 20 constituting a bolt shaft 21, a bolt head 11, and a tapered cylindrical body portion 12 and surrounded by the tapered cylindrical body portion 12.
  • the head member 10 provided with a convex portion 15a protruding in a short cylindrical shape so that the end surface thereof becomes a joint surface for friction welding is formed as a separate part.
  • Such a manufacturing process of separately producing the shaft member 20 and the head member 10 can be easily performed by a conventional method of manufacturing a screw material (fastening member).
  • the shaft member 20 and the head member 10 are joined by friction welding (see FIG. 2), and the annealing process is performed on the pressure contact portion 16 by the friction welding.
  • tensile_strength test was done about the locking bolt 10 manufactured in this way, it has confirmed that the intensity
  • plastic deformation occurred in the middle part of the bolt shaft 21, and the press contact part 16 was not divided or damaged.
  • this method of manufacturing the locking bolt 10 it is sufficiently long (deep) in the axial direction as compared with a manufacturing method in which the tapered cylindrical portion 12 is cut and formed by cutting or a manufacturing method in which it is formed by forging. Suitable for form, cheaper and more rational production.
  • the friction welding described above is one of applied technologies for joining metals to each other using heat generated by friction.
  • two base materials are brought into contact with each other to cause relative rotational movement, and thrust is applied to generate frictional heat on the contact surface.
  • the butted surfaces and the vicinity thereof are softened by the heat, and when the pressure is reached, the relative motion is stopped and the pressure thrust is further increased to join the two base materials.
  • the tapered cylindrical portion 12 may be softened and deformed.
  • the inner bottom portion 15 is close to the pressure contact portion 16 generated by friction welding between the outer peripheral surface 15b of the convex portion 15a and the inner peripheral surface 12a of the tapered cylindrical body portion (see FIG. 2). ) Is formed. Since the side 23 is accommodated in this space, the appearance of the bolt 100 from the axial direction does not deteriorate.
  • the offset 23 is generated from the contact surfaces of the head member and the shaft member and is formed in a curl shape. Further, the corners of the end surface of the convex portion 15a are chamfered so that the offset 23 is suitably wound around. As described above, since the offset 23 has a shape that is suitably formed, the area of the joint portion (pressure contact portion 16) by friction welding can be appropriately expanded as shown in FIG. 2, and the joint strength is increased. be able to.
  • the joint surface 15a ′ of the convex portion 15a in the inner bottom portion 15 of the bolt head 11 surrounded by the tapered cylindrical portion 12 in the head member 10 is formed flat, and the joint surface 15a.
  • the joint end surface 22 of the bolt shaft 21 that is friction-welded to the ' is formed flat. According to this, it is easy to manufacture the shaft member 20 and the head member 10 with a simple shape, and the tapered cylindrical body portion 12 can be appropriately formed to a sufficient depth to enhance the loosening prevention effect.
  • the solid phase diffusion bonding is also suitably performed, and a locking bolt having a required function and strength can be produced appropriately and inexpensively.
  • the joint surface 15a ′ of the convex portion 15a in the inner bottom portion 15 and the joint end surface 22 of the bolt shaft 21 are formed in the same shape and the same diameter.
  • the inner peripheral surface 12a of the tapered cylindrical portion 12 is provided on a conical curved surface, and the outer peripheral surface of the tapered cylindrical portion 12 stands substantially vertically from the fastened body 40.
  • the rising surface 12c and the concave curved surface 12b continuous with the rising surface are formed. According to the form in which the standing surface 12c and the concave curved surface 12b are continuous, the strength of the peripheral edge portion on the seating surface 13 side of the tapered cylindrical portion 12 can be appropriately ensured.
  • the size of the rising surface 12c is set to a thickness corresponding to the washer or more, sufficient strength can be obtained.
  • the thickness of the tapered cylindrical portion 12 is set so as to be equal or gradually increased from the portion on the head 11 side of the bolt that starts the diameter expansion to the portion that changes from the concave curved surface 12b to the standing surface 12c.
  • the thick portion between the upright surface 12c and the inner peripheral surface 12a can perform the same function as the washer and maintain the loosening prevention performance, while appropriately reducing the outer dimensions.
  • the joint surface 15c of the convex portion in the inner bottom portion 15 of the head 11 of the bolt surrounded by the tapered cylindrical portion 12 in the head member 10 is formed as a concave curved surface.
  • a joint end surface 22c of the bolt shaft 21 friction-welded to 15c is formed in a convex curved surface. Since the joint area by friction welding can be increased, there is an advantage of increasing the joint strength. Also by this, the solid-phase diffusion bonding of the mutual members (the shaft member 20 and the head member 10) by friction welding is also suitably performed, and the loosening bolt having the required function and strength can be produced appropriately and inexpensively.
  • the shape of the joint surface in the inner bottom 15 of the bolt head 11 and the joint end surface of the shaft member 20 is not particularly limited as long as it satisfies the specifications for the function and strength of the manufactured locking bolt. Good.
  • the end portion 21a on the side where the joining end face 22 of the shaft member 20 is provided may be formed thin. According to this, it is possible to more reliably prevent the contact 23 (see FIG. 2) of the press contact portion 16 caused by the friction welding from coming into contact with the inner peripheral surface 12a (see FIG. 1) of the tapered cylindrical portion 12. it can. Therefore, production efficiency can be improved. If the diameter of the end portion 21a is made larger than the root diameter of the screw, the end portion 21a does not become the minimum diameter portion of the bolt shaft 21, so that sufficient strength can be secured.
  • the seat surface side of the tapered cylindrical portion integrally formed as the flange portion is formed in the same manner as the shape of the seating surface 13 side of the locking bolt 100 according to the present invention. That is, the locking nut 300 is provided so as to surround a bolt shaft to which the nut is integrally screwed from the nut head 31 so as to gradually expand in diameter concentrically with the bolt shaft, and an end surface of the bolt 41 is fastened.
  • a tapered cylindrical portion 32 provided as a seating surface 33 in contact with (see FIG. 14) is provided, and an inner peripheral surface 32a of the tapered cylindrical portion is provided in a conical shape and an outer peripheral surface of the tapered cylindrical portion. At least a portion of which is provided on the concave curved surface 32b.
  • the outer peripheral surface of the tapered tubular portion 32 is formed by a standing surface 32c that stands substantially vertically from the fastened body 41 and a concave curved surface 32b that continues to the standing surface.
  • a standing surface 32c that stands substantially vertically from the fastened body 41 and a concave curved surface 32b that continues to the standing surface.
  • the concave curved surface 32b and the seating surface 33 The standing length of the standing surface 32c is set so that the thickness between the two can be secured without undergoing plastic deformation of the tightening force of the nut and the impact and vibration caused by the fastened body.
  • the standing length (thickness) is set to a standard flat washer thickness or more than that specified in the JIS standard.
  • the strength of the peripheral edge portion of the tapered cylindrical portion 32 on the seating surface 33 side can be appropriately ensured.
  • a sufficient strength can be obtained when the size of the standing surface 32c is set to a thickness corresponding to the washer or more. That is, it is possible to receive the force caused by the shock and vibration caused by the fastened body 41 on the seat surface 33 without plastic deformation of the thick portion surrounded by the standing surface 32c and the inner peripheral surface 32a. Then, the received force is transmitted to the concave curved surface 32b continuous with the upright surface 32c, and the concave curved surface 32b is caused to bend. As a result, the rotation of the loosening prevention nut 300 can be suppressed so that no loosening occurs.
  • the tapered cylindrical body portion 32 can be appropriately elastically deformed by the tightening force, and the elastic stress generated thereby acts to absorb impacts and vibrations, thereby producing a suitable loosening prevention effect.
  • the outer dimension can be appropriately reduced while the thick portion between the rising surface 32c and the inner peripheral surface 32a performs the same function as the washer and maintains the loosening prevention performance.
  • FIG. 14 shows a state in which the fastened bodies 40 and 41 are fixed by the loosening bolt 100 and the loosening nut 300.
  • the locking nut 300 is screwed to the shaft of the locking bolt, and the fastened bodies 40 and 41 can be firmly fixed between the bolt side and the nut side.
  • a loosening prevention bolt 100 and a loosening prevention nut 300 are fastened and fixed via a washer 51 to a vibration barbell (fastened body 40) provided on a vibration table 50 of a high-speed screw loosening tester.
  • a vibration barbell fastened body 40
  • a vibration table 50 of a high-speed screw loosening tester Set in the state.
  • Each of the M10, M12, and M16 screws was tested in a state where it was fastened with a tightening force of JIS standards.
  • the screw looseness test using this high-speed screw looseness tester is performed for a maximum of 17 minutes under the conditions that the vibration frequency is 1780 rpm, the vibration table stroke is 11 mm, the impact stroke is 19 mm, and the vibration direction is perpendicular to the bolt axis. Is to measure.
  • This high-speed slack test is a device that repeatedly applies vibrations and shocks at a high speed, and a normal bolt or nut loosens within a few seconds to a few tens of seconds. Further, even a double nut structure that is said to have the highest tightening holding force currently on the market can only be held for several minutes. By maintaining the tightening force for 17 minutes by this test method, it was confirmed that the configuration of the fastener using the locking bolt 100 and the locking nut 300 according to the present invention has the highest performance. .
  • FIGS. 16 to 21 show an example of a loosening prevention nut in which the inner peripheral surface 12a of the tapered cylindrical portion 12 is formed by a concave curved surface.
  • the shape of the inner peripheral surface 12a of the tapered cylindrical portion 12 can be applied to the shape of the head member 10 of the locking bolt as in the embodiments of FIGS.
  • the shape of the concave curved surface of the inner peripheral surface 12a of the tapered cylindrical portion 12 is not limited to a concave surface curved in a normal arc shape whose cross section is constituted by a part of a circular curve, and for example, a catenary curve (catenary curve).
  • the inner peripheral surface 12a of the tapered cylindrical portion 12 is formed by a concave curved surface, so that the seating surface, which is the end surface of the tapered cylindrical portion 12, is extremely opposed to the body to be fastened. Can be pressed evenly. That is, the tightening force of the fastener composed of bolts and nuts is evenly distributed and converted into an equal pressure on the fastened body, and the entire surface of the seating surface can be effectively used to prevent loosening. Thereby, the loosening prevention effect can be further improved.
  • the taper cylindrical body portion 32 is provided so that the taper angle is an acute angle.
  • the body to be fastened is set so that the outer diameter of the seating surface 33 is within a range in which surface pressure is generated so that the seat surface 33 is effectively pressed against the body 41 to be fastened.
  • An upright surface 32 c that stands vertically from 41 is provided. According to this, the diameter of the seating surface 33 can be appropriately reduced without reducing the loosening prevention effect.
  • the fastening force is converted into the surface pressure, and the surface pressure tends to be concentrated only on the inner peripheral edge of the seating surface of the fastening member.
  • the surface pressure can be generated over the entire seat surface, and the tightening force can be more dispersed.
  • the effect of preventing the loosening can be enhanced by the action of the tapered cylindrical portion.
  • the surface pressure gradually decreases on the outer peripheral side of the seat surface, and no surface pressure is applied on the outer side of a certain position on the outer peripheral side.
  • the outer diameter of a seat surface can be set appropriately and the fastening member concerning this invention can be formed compactly.
  • FIG. 26 is a diagram showing the analysis result of the surface pressure when the outer diameter of the seating surface is set to an appropriate diameter of 20 mm with respect to the bolt of M10, and FIG. It shows the analysis result of surface pressure in the case of. 26, when the load (axial force) applied to the bolt shaft is 33700 N, the normal stress (surface pressure) applied to the seating surface 33 is 5 at the inner edge portion. .9 ⁇ 10 8 Pa, gradually decreasing toward the outside as represented by the stepwise shade, and a minimum of 4.3 ⁇ 10 7 Pa at the outer edge.
  • the load axial force
  • surface pressure surface pressure
  • the surface pressure applied to the seating surface 33 becomes the maximum 6.1 ⁇ 10 8 Pa at the inner edge, and gradually toward the outside.
  • the surface pressure is zero and the surface is floated at the portion where the outer edge portion is expressed most darkly.
  • the maximum surface pressure at the inner edge is 2.5 ⁇ 10 9 Pa, which is wider at the outer edge.
  • the part is in a floating state, and the surface pressure is clearly uneven as compared with the present invention (see FIG. 28).
  • the inner peripheral surface 12a of the tapered cylindrical portion 12 is formed by a concave curved surface, so that the same loosening prevention effect as that of the nut or bolt described above can be obtained.
  • This washer is used together with bolts and nuts as a fastening member used when fastening a body to be fastened using a screw tightening action, and is a circular flat band concentric with the shaft so as to be pressed against the body to be fastened.
  • a tapered cylindrical portion formed in a cylindrical shape that gradually increases in diameter toward a seat surface provided in a ring shape is provided.
  • the washer is used to prevent the slack from being sandwiched between the fastening member and the body to be fastened when the body to be fastened is fastened by using a screw fastening action of a bolt or nut fastening member.
  • the washer is excellent in the shape of a cylinder whose diameter gradually increases from a pressed contact surface 60 (see FIG. 34) to which the seat surface of the fastening member is pressed to the washer seat surface 13 pressed against the fastened body.
  • the formed tapered cylindrical portion 12 and the pressure contact surface 60 are provided with a plurality of convex portions 61 so as to prevent co-rotation of the fastening member.
  • the projections of the plurality of convex portions 61 of the washer have an inner surface formed in a linear plane corresponding to the head of the hexagon bolt and nut, and an outer surface formed in an arc shape. It is not limited to the form, and any form that can prevent the joint members from rotating together is acceptable.
  • the convex part 61 as shown in FIG. 29 may be provided in three places equally in the circumference, and the form of the convex part may be further divided into a plurality of parts.
  • the upper end edge (inner peripheral edge) of the through hole 62 of the washer is chamfered to form a chamfered portion 63, and the bolt shaft is inserted without interfering with the R portion continuous from the head of the bolt to the shaft. And can fit properly.
  • the inner peripheral edge portion in which the chamfered portion 63 is formed the inner diameter can be regulated so that the thickness between the pressure contact surface 60 and the inner peripheral surface 12a is small and the bolt can be centered, and the bolt It is in a form that is easy to get used to.
  • FIG. 35 shows a loosening washer 500 in which the seating surface is formed by following an arcuate curved surface so as to fit a curved surface 600 which is an outer peripheral surface of a cylinder or a pipe.
  • the slack stopper washer 500 can be appropriately disposed. Also by this, the outstanding anti-slack effect can be acquired similarly to what was demonstrated above.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bolts, Nuts, And Washers (AREA)
  • Standing Axle, Rod, Or Tube Structures Coupled By Welding, Adhesion, Or Deposition (AREA)
  • Connection Of Plates (AREA)
PCT/JP2012/083027 2011-12-22 2012-12-20 締結部材 Ceased WO2013094672A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP12860487.3A EP2796734B1 (en) 2011-12-22 2012-12-20 Fastening member
US14/367,834 US9212682B2 (en) 2011-12-22 2012-12-20 Fastening member
JP2013550323A JP5787197B2 (ja) 2011-12-22 2012-12-20 締結部材
KR1020147019735A KR101985316B1 (ko) 2011-12-22 2012-12-20 체결부재

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2011281019 2011-12-22
JP2011-281019 2011-12-22
JP2012-143978 2012-06-27
JP2012143978 2012-06-27

Publications (1)

Publication Number Publication Date
WO2013094672A1 true WO2013094672A1 (ja) 2013-06-27

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US (1) US9212682B2 (enExample)
EP (1) EP2796734B1 (enExample)
JP (3) JP5555308B2 (enExample)
KR (1) KR101985316B1 (enExample)
WO (1) WO2013094672A1 (enExample)

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US11338385B2 (en) * 2015-10-29 2022-05-24 Komatsu Ltd. Machine component and method for producing the same
JP7584366B2 (ja) 2021-07-16 2024-11-15 日立Astemo株式会社 溶接部材および緩衝器

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PL3097315T3 (pl) 2014-01-24 2022-04-19 Kenco AU Pty Ltd Nakrętka zabezpieczająca i podkładka
US9897132B2 (en) * 2015-06-02 2018-02-20 Northrop Grumman Systems Corporation Diffusion bonded fastener assembly
US10876569B2 (en) 2015-07-28 2020-12-29 Kenneth Maxwell Archer Locking nut or bolt and washer
CA2978485C (en) * 2015-08-27 2019-03-26 Arconic Inc. Fastener locking members
CN105465147A (zh) * 2015-11-30 2016-04-06 苏州迪诺环保科技有限公司 一种组合螺钉
CN105757096A (zh) * 2016-03-31 2016-07-13 南通康达鑫电子有限公司 一种防松螺母
GB201618301D0 (en) * 2016-10-28 2016-12-14 Excalibur Screwbolts Ltd Improvements in or relating to screwbolts
JP6590263B2 (ja) * 2017-03-06 2019-10-16 建三 山本 自動車用ホイールナット
US10773817B1 (en) 2018-03-08 2020-09-15 Northrop Grumman Systems Corporation Bi-directional flow ram air system for an aircraft
JP7344823B2 (ja) * 2020-03-19 2023-09-14 本田技研工業株式会社 ボルト

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Publication number Priority date Publication date Assignee Title
US11338385B2 (en) * 2015-10-29 2022-05-24 Komatsu Ltd. Machine component and method for producing the same
JP7584366B2 (ja) 2021-07-16 2024-11-15 日立Astemo株式会社 溶接部材および緩衝器

Also Published As

Publication number Publication date
JPWO2013094672A1 (ja) 2015-04-27
KR101985316B1 (ko) 2019-06-03
JP5950003B2 (ja) 2016-07-13
JP5787197B2 (ja) 2015-09-30
EP2796734A1 (en) 2014-10-29
JP2014029200A (ja) 2014-02-13
KR20140100578A (ko) 2014-08-14
JP5555308B2 (ja) 2014-07-23
JP2015180840A (ja) 2015-10-15
US20150016920A1 (en) 2015-01-15
EP2796734B1 (en) 2019-10-30
US9212682B2 (en) 2015-12-15
EP2796734A4 (en) 2016-01-13

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