WO2016006598A1 - Corps fileté mâle, élément d'assemblage, corps fileté femelle, et structure de fixation de corps filetés - Google Patents

Corps fileté mâle, élément d'assemblage, corps fileté femelle, et structure de fixation de corps filetés Download PDF

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Publication number
WO2016006598A1
WO2016006598A1 PCT/JP2015/069500 JP2015069500W WO2016006598A1 WO 2016006598 A1 WO2016006598 A1 WO 2016006598A1 JP 2015069500 W JP2015069500 W JP 2015069500W WO 2016006598 A1 WO2016006598 A1 WO 2016006598A1
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WO
WIPO (PCT)
Prior art keywords
male screw
screw body
female
washer
male
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/JP2015/069500
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English (en)
Japanese (ja)
Inventor
裕 道脇
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Nejilaw Inc
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Nejilaw Inc
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Publication date
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Priority to JP2016532941A priority Critical patent/JP6715455B2/ja
Publication of WO2016006598A1 publication Critical patent/WO2016006598A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B39/00—Locking of screws, bolts or nuts
    • F16B39/22—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening
    • F16B39/28—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening by special members on, or shape of, the nut or bolt
    • F16B39/30—Locking exclusively by special shape of the screw-thread

Definitions

  • the present invention relates to a fastening structure using a male screw body, a cooperating member, a female screw body, and the like, and particularly to a fastening structure suitable for preventing reverse rotation of the screw body.
  • screw bodies have been used to fasten objects to be fastened in various situations.
  • This screw body has a structure in which a male screw body in which a spiral groove is formed on a columnar outer periphery and a female screw body in which a spiral groove is formed on the inner periphery of a cylindrical member are screwed together.
  • a washer is inserted around the male screw body when the screw body is fastened.
  • This washer protects the object to be fastened from buckling or scratches at the time of fastening, and conversely suppresses loosening of the screw body by positively pressing the object to be fastened.
  • the washer has a general ring-shaped “flat washer” and a protrusion extending in the radial direction on the inner periphery and outer periphery, and is engaged with a member to be fastened or a screw body to prevent loosening.
  • teeth around the fastening surface There is a “toothed washer” and so on.
  • An object of the present invention is to provide a fastening structure that prevents reverse rotation, that is, prevents loosening.
  • the present invention for achieving the above object is a male screw body characterized in that a male screw side cooperation region having a non-circular cross section when viewed from the axial direction is formed in a shaft portion having a male screw portion.
  • the male screw side cooperation region is formed to overlap the male screw portion.
  • the male screw side cooperation region is formed so as to overlap the male screw portion by forming a shape in which a part of the screw thread in the male screw portion is omitted.
  • the male screw side cooperation region has an abbreviated shape with an upper limit of three-fourths of the thread height in the male screw portion.
  • the male screw side cooperation region is formed so as to overlap with a base portion on the base end side with respect to the male screw portion.
  • the maximum distance from the axial center of the male screw side cooperation region in the base portion is larger than the maximum distance from the axial center of the male screw portion.
  • the minimum distance from the axial center of the male screw side cooperation region in the base portion is larger than the maximum distance from the axial center of the male screw portion.
  • the male screw side cooperation region is engaged with a cooperation member inserted into the shaft portion in a circumferential direction.
  • an axial distance that engages with a cooperation member inserted into the shaft portion in the male screw side cooperation region is equal to or greater than a pitch of a thread of the male screw portion.
  • the axial distance to engage with the cooperation member inserted into the shaft part is at least twice the pitch of the thread of the male screw part.
  • the male screw side cooperation region is formed in a spiral shape.
  • the present invention that achieves the above object is a cooperating member in which a through-hole through which a male screw portion of a male screw body can be inserted is formed, wherein the through-hole has a non-circular shape and is screwed with the male screw body It is a cooperation member characterized by having the engaging mechanism engaged with the female screw body to perform in the peripheral direction.
  • the axial distance of the through hole is greater than or equal to the pitch of the thread of the male screw body.
  • the axial distance of the through hole is more than twice the pitch of the thread of the male screw body.
  • the axial distance of the through hole is more than three times the pitch of the thread of the male screw body.
  • the engagement mechanism In connection with the cooperation member, the engagement mechanism has a plurality of irregularities in the circumferential direction.
  • the surface facing the female screw body is a conical tapered surface whose axial center is convex toward the female screw body.
  • the engagement mechanism for the female screw body is formed on both axial surfaces.
  • the link member is a washer.
  • the present invention that achieves the above object is an internal thread body in which an internal thread side cooperation region having a non-circular cross section when viewed in the axial direction is formed in a cylindrical portion having an internal thread portion.
  • the minimum distance from the axial center of the female screw side cooperation region is larger than the minimum distance from the axial center of the female screw portion.
  • the female screw side cooperation region is engaged with a shaft portion of the male screw body in a circumferential direction.
  • the female screw side cooperation region is elastically deformable in the radial direction.
  • the present invention that achieves the above object has a male screw body in which a male screw side cooperation region having a non-circular cross section when viewed from the axial direction is formed in a shaft portion having a male screw portion, and a through-hole through which the male screw portion can be inserted.
  • a formed cooperative member that engages in the circumferential direction with the male screw side cooperative region by forming the through hole in a non-circular shape, and engages in a circumferential direction with a female screw body that is screwed with the male screw body
  • a screw body fastening structure comprising: a cooperating member characterized by having an engaging mechanism.
  • the cooperation member has the engagement mechanism with the female screw body on both surfaces in the axial direction, and the female screw body has both sides in the axial direction of the cooperation member.
  • the female screw body is engaged with the cooperation member in the circumferential direction.
  • the present invention that achieves the above object includes a male screw body in which a male screw side cooperation region having a non-circular cross-section when viewed from the axial direction is formed in a shaft portion having a male screw portion, and a female screw portion that is screwed with the male screw portion. And a female screw body in which a female screw side cooperative region having a non-circular cross section when viewed in the axial direction is formed, and the male screw side cooperative region and the female screw side cooperative region allow relative rotation by an external force.
  • the screw body fastening structure is characterized in that they are structured to engage with each other in the circumferential direction.
  • the screw body can be reliably prevented from loosening by preventing the screw body from rotating backward, for example, by preventing the screw body from rotating in the direction in which the screw body is loosened. Become.
  • FIG. 1A is a front sectional view of a washer, (B) a bottom view of a washer, (C) a top view of an internal thread body, and (D) a front view of an internal thread body of a fastening structure of a thread body according to a first embodiment of the present invention. is there.
  • FIG. 1 It is a figure which shows the state in the middle of the fastening of the fastening structure of the screw body which concerns on 1st embodiment of this invention.
  • (A) is the fastening state figure of the internal thread body and washer of the fastening structure of the screw body which concerns on 1st embodiment of this invention
  • or (D) is a figure which shows the modification.
  • or (C) are the fastening state figures of the internal thread body and washer of the fastening structure of the thread body which concern on the modification of 1st embodiment of this invention.
  • or (D) are the front views and bottom views of a male screw body of the fastening structure of the screw body which concerns on the modification of 1st embodiment of this invention.
  • FIG. 1 It is a fragmentary sectional view which shows the fastening structure of the screw body which concerns on 3rd embodiment of this invention. It is (A) sectional drawing, (B) front view, and (C) bottom view which show the internal thread body used with the fastening structure of the thread body concerning 3rd embodiment of this invention. (A) And (B) is the front view and bottom view which show the modification of the external thread body used with the fastening structure of the thread body which concerns on embodiment of this invention. It is (A) top view, (B) front view, (C) bottom view, (D) side view of the external thread body used with the fastening structure of the thread body concerning 4th embodiment of this invention. It is a top view which expands and shows a part of the same male screw body.
  • FIG. 1 shows a fastening structure of a screw body according to the first embodiment.
  • the fastening structure of the screw body includes a male screw body 10, an annular washer 50 serving as a link member, a fastened member 80, and a female screw body 90.
  • the male screw body 10 is a so-called bolt and has a head 20 and a shaft 30.
  • a screw body side seat portion 22 is formed at a portion corresponding to a lower portion or a root of the head 20.
  • the shaft portion 30 is formed with a so-called cylindrical portion 30a and a male screw portion 30b having a columnar shape.
  • the cylindrical part 30a here, you may define as a base part.
  • the shaft portion 30 is formed with a male screw side cooperation region 35 having a non-circular cross section when viewed from the axial direction.
  • the male screw side cooperation region 35 is formed so as to overlap the cylindrical portion 30a.
  • the male screw side cooperation region 35 has a shape in which a part of a circular arc having a circular cross section is omitted along the string (an irregular shape), and the string portion is connected to the male screw side contact portion 120.
  • the male screw side contact portion 120 is a plane that is perpendicular to the radial direction and directed outward in the radial direction on the peripheral surface of the shaft portion 30.
  • the male screw side contact portion 120 varies in distance from the screw shaft center along the circumferential direction, and the first male screw side contact region 120Y has distances X1, X2 along one circumferential direction X of the male screw body 10. Becomes larger. In the second male screw side contact region 120X, the distances Y1 and Y2 increase along the other circumferential direction Y of the male screw body 10. Note that the amount of variation is set to be the same as that of a washer-side contact portion 110 described later if a slight margin is ignored. Alternatively, the margin clearance may be set so as to be filled by deformation in the direction perpendicular to the axis caused by axial compression caused by tightening of the washer 50 by the female screw 90.
  • the minimum radius 35Y from the axis of the male screw side cooperation region 35 is set to be equal to or greater than the maximum radius 30bX from the axis of the male screw portion 30b. Therefore, the maximum radius 35Y from the axis of the male screw side cooperation region 35 is preferably set to be larger than the maximum radius 30bX from the axis of the male screw portion 30b.
  • a first receiving portion 60 is formed on one surface of the washer 50.
  • the first receiving portion 60 faces the seat portion 92 of the female screw body 90, and a first engagement mechanism A is configured between the two.
  • the first engagement mechanism A when at least the female screw body 90 tries to rotate in a loosening direction with respect to the male screw body 10 to be screwed, the first receiving portion 60 and the seat portion 92 of the female screw body 90 are engaged with each other. And the relative rotation of the 1st receiving part 60 and the screw body side seat part 22 with respect to the said rotation direction is prevented.
  • a second receiving portion 70 is formed on the other side of the washer 50. The second receiving part 70 faces the fastened member 80.
  • the through hole 52 of the male screw body in the washer 50 has a non-circular shape when viewed from the axial direction.
  • the through hole 52 has a shape in which a part of a circular arc of a regular circle is omitted along the string, and engages with the male screw side cooperation region 35 of the male screw body 10 in the circumferential direction (support this). Defined as engagement mechanism B).
  • the auxiliary engagement mechanism B includes a washer side abutting portion 110 formed in the through hole 52 of the washer 50 and a male screw side abutting portion 120 formed in the male screw side cooperation region 35 of the male screw body 10.
  • the through hole 52 of the washer 50 has a partial arc shape that is concentric with the axis of the screw, and the remaining portion is cut into a straight line like a string. The string becomes the washer side contact portion 110. Therefore, the inner wall of the through hole 52 of the washer 50 has a planar shape at a portion corresponding to the washer-side contact portion 110, and the distance from the screw axis varies along the circumferential direction.
  • the distances XA and XB increase along one circumferential direction X of the washer 50.
  • the distances YA and YB increase along the other circumferential direction Y of the washer 50.
  • the portion excluding the washer-side contact portion 110 has a perfect circular shape with a constant distance from the screw shaft center.
  • the minimum radius 52Y from the axis of the through hole 52 is set to be equal to or larger than the maximum radius 30bX of the male screw portion 30b. As a result, the through hole 52 and the male screw part 30b of the male screw body 10 do not have to interfere with each other.
  • both the washer side contact portion 110 and the male screw side contact portion 120 come into contact with each other, and the screw shaft centers are aligned.
  • the relative rotation in the circumferential direction is restricted. That is, the washer side contact portion 110 and the male screw side contact portion 120 act as the auxiliary engagement mechanism B.
  • the first receiving portion 60 of the washer 50 is formed with a first receiving portion side unevenness 64 that engages with the screw body side unevenness 94.
  • corrugation 64 becomes the saw blade shape provided in multiple numbers by the circumferential direction continuously.
  • the direction in which each of the first receiving portion side irregularities 64 extends, that is, the direction in which the ridge line extends, is along the radial direction of the washer 50. As a result, the first receiving portion side unevenness 64 extends radially from the center of the through hole 52 of the washer 50.
  • the first receiving portion 60 is formed with a washer side tapered surface inclined in the radial direction.
  • the washer-side taper surface is inclined and shaped like a mortar so that the center side approaches the head 20 side of the male screw body 10 (see FIG. 1), resulting in a concave conical shape.
  • the first receiving portion side irregularities 64 described above are formed on the washer side tapered surface.
  • the cylindrical portion 96 of the female screw body 90 is formed with a female screw portion 96 a for screwing with the male screw body 10. Further, the female screw body 90 is formed with a seat portion 92 that faces the first receiving portion 60 of the washer 50.
  • the seat portion 92 and the first receiving portion 60 on the washer 50 side are both annular surface regions, and abut against each other to play a role of transmitting a fastening force (axial force) to the fastened member 80. That is, most of the axial force in the fastening structure is transmitted to the fastened member 80 through the washer 50.
  • a screw body side unevenness 94 is formed in the seat portion 92 of the female screw body 90.
  • the screw body side unevenness 94 has a saw blade shape that is continuously provided in the circumferential direction.
  • the direction in which each of the threaded body side irregularities 94 extends, that is, the direction in which the ridge line extends is the radial direction of the female threaded body 90.
  • the screw body side unevenness 94 extends radially from the axis.
  • the threaded body side seat portion 92 is formed with a threaded body side tapered surface inclined in the radial direction. Since the screw body side tapered surface is inclined so that the center side approaches the washer 50 side, as a result, a convex conical shape is formed on the head 20 side of the male screw body 10. The aforementioned threaded body side unevenness 94 is formed on the threaded body side tapered surface.
  • the screw body side unevenness 94 and the first receiving portion side unevenness 64 are formed in a saw blade shape that is continuous in the circumferential direction, it acts as a so-called ratchet mechanism or one-way clutch mechanism. To do.
  • the relative movement of the screw body side unevenness 94 and the first receiving portion side unevenness 64 of the washer 50 is allowed to realize smooth relative rotation.
  • the relative movement of the screw body side unevenness 94 and the first receiving portion side unevenness 64 of the washer 50 is completely restricted. As a result, workability at the time of fastening and subsequent locking can be rationally achieved.
  • the screw body side seat portion 92 and the first receiving portion 60 are formed with the screw body side taper surface and the washer side taper surface, so that the contact area between both can be increased.
  • the fastening force in the axial direction by this fastening structure also acts in the radial direction by the tapered surface. By pressing the taper surfaces of each other in the radial direction, centering can be carried out by self-excitation. As a result, the concentricity of the female screw body 90 and the washer 50 is increased, and the engagement accuracy between the screw body side unevenness 94 and the first receiving portion side unevenness 64 can be increased.
  • the auxiliary engagement mechanism B avoids the shapes of the washer-side contact portion 110 and the male screw-side contact portion 120 from being concentric circles with respect to the screw shaft center.
  • the shapes of the washer-side contact portion 110 and the male screw-side contact portion 120 vary along the circumferential direction in the distance from the screw shaft center.
  • both sawtooth shapes in the first engagement mechanism A are such that when the female screw body 90 tries to rotate in the fastening direction Y, the inclined surfaces 24Y and 64Y contact each other, Relative sliding is allowed while narrowing the distance between the two in the axial direction.
  • the vertical surfaces (surfaces with a strong inclination) 94X and 64X come into contact with each other to prevent relative movement between the two.
  • the engagement between the screw body side unevenness 94 and the first receiving portion side unevenness 64 becomes stronger.
  • the engagement strength on the loosening direction X side is increased.
  • the inclination angle of the screw body side taper surface and the inclination angle of the washer side taper surface are made different from each other.
  • the inclination angle from the axis of the washer side taper surface is set to the inclination angle from the axis of the screw body side taper surface.
  • the first engagement is provided between the screw body side seat portion 92 of the female screw body 90 and the first receiving portion 60 of the washer 50 by interposing the washer 50.
  • an auxiliary engagement mechanism B is formed between the through hole 52 of the washer 50 and the male screw side cooperation region 35 of the male screw body 10.
  • the fastening state which does not loosen at all can be obtained.
  • the one-way clutch structure of the first engagement mechanism A allows the relative rotation of the washer 50 and the female screw body 90. Is freely possible.
  • the screw body side unevenness 94 and the first receiving portion side unevenness 64 have a saw blade shape is illustrated as the first engagement mechanism A, but the present invention is not limited to this.
  • the unevenness of each other can be formed in a mountain shape (both are inclined surfaces). In this way, when the female screw body 90 rotates in the loosening direction X, the inclined surfaces 94X and 64X tend to move relative to each other. The screw body side unevenness 94 and the first receiving portion side unevenness are along this inclined surface. 64 tries to leave.
  • this moving distance (separation angle ⁇ ) is set to be larger than the lead angle of the female screw body 90, the screw body side unevenness 94 and the first receiving part side unevenness 64 are more likely to be separated even if the female screw body 90 tries to loosen. You will not be able to relax.
  • FIG. 5 (B) an isosceles triangle-shaped concavity and convexity are shown as an example.
  • the inclination angle of the inclined surfaces 94Y and 64Y that abut at the time of fastening rotation is larger than that at the time of loose rotation. It is also preferable to make the inclination angles of the inclined surfaces 94X and 64X in contact with each other gentle. In this way, since the circumferential distance P between the inclined surfaces 94Y and 64Y that must be overcome during fastening rotation can be shortened, play (gap) after fastening can be reduced.
  • corrugated irregularities with curved ridges and valleys are also preferable. Smooth operability can be obtained during fastening.
  • the unevenness extending in the radial direction is exemplified, but it is also preferable to form a spiral (spiral) groove or mountain (unevenness) as shown in FIG.
  • FIG. 6B even a groove or mountain (unevenness) extending linearly can be inclined so that the circumferential phase changes with respect to the radial direction of the screw.
  • FIG. 6C it is also preferable to adopt a so-called embossed shape in which a plurality of fine irregularities are formed both in the circumferential direction and the radial direction (planar shape) of the screw.
  • the uneven shapes of the screw body side unevenness 94 and the first receiving portion side unevenness 64 coincide (similar).
  • different shapes from the various shapes in FIGS. 5 and 6 can be selected and combined with each other.
  • the threaded body side tapered surface is convex and the washer side tapered surface is concave is illustrated, but the present invention is not limited to this.
  • the threaded body side taper surface can be concave and the washer side taper surface can be convex.
  • both can be non-tapered surfaces perpendicular to the screw axis.
  • a tapered surface may be formed on only one of the female screw body 90 and the washer 50.
  • the basic shape of the washer 50 is preferably a so-called spring washer shape or a disc spring shape in which a spiral shape is used.
  • the male screw body 10 of the first embodiment has exemplified the case where a groove (constriction) is provided at the boundary between the cylindrical portion 30a and the male screw portion 30b
  • the present invention is not limited to this.
  • a structure in which the cylindrical portion 30a and the male screw portion 30b are continuous without a groove is also preferable, and the strength of the male screw body 10 can be increased.
  • the male screw side contact portion 120A may be formed.
  • a protrusion 120B that protrudes radially outward from the periphery of the cylindrical portion 30a may be formed as the male screw side cooperation region 35 of the male screw body 10.
  • the cylindrical portion 30a may be a polygonal section 120C (here, a hexagon) as the male screw side cooperation region 35 of the male screw body 10.
  • the cylindrical portion 30a may have an elliptical cross section 120D as the male screw side cooperation region 35 of the male screw body 10. All of them have a “non-circular cross section” shape.
  • the through hole 52 of the washer 50 has a similar shape corresponding to these, but it is necessary to make both the shapes similar if they can be engaged in the circumferential direction. Absent.
  • the male screw body 10 is formed with a male screw side cooperation region 35 so as to overlap with the male screw portion 30b.
  • the male screw side cooperation region 35 is such that a part of a circular arc of a cross section formed along the apex of the thread is omitted (or cut) along the chord. It has a shape, and this string portion becomes the male screw side contact portion 120. That is, by omitting a part of the screw thread so as to be continuous in the axial direction, a virtual plane P that is perpendicular to the radial direction and directed outward in the radial direction is configured, and this virtual plane P is the male screw side contact portion 120. It becomes. Therefore, the minimum radius 35Y of the male screw side cooperation region 35 is set to be smaller than the maximum radius 30bX of the male screw portion 30b.
  • the thread thread valley bottom 30 ⁇ / b> C remains around the axial direction of the male screw contact portion 120.
  • the function of screwing into the female screw body 90 remains.
  • the male thread side contact portion 120 it is preferable to omit the upper limit of two-thirds of the thread height, and more preferably, omit the upper limit of one-half of the thread height.
  • the minimum radius (minimum distance) 35Y of the male screw side cooperation region 35 is larger than the minimum radius (valley bottom radius) 30bY from the axis of the male screw portion 30b.
  • the male screw side contact portions 120 are formed at three locations that form a phase difference of 120 degrees in the circumferential direction.
  • the through hole 52 through which the male screw body of the washer 50 can be inserted has a non-circular shape when viewed from the axial direction.
  • the through hole 52 has a partial arc shape that is concentric with the axial center of the screw and has a shape in which the remaining portion is linearly cut off like a string. 110.
  • the washer-side abutting portions 110 are formed in three places that have a phase difference of 120 degrees in the circumferential direction.
  • the washer side abutting portion 110 abuts on the male screw side abutting portion 120 of the male screw side cooperation region 35 to engage with each other in the circumferential direction to constitute the auxiliary engagement mechanism B.
  • An auxiliary engagement mechanism B can be configured between the regions 35. Accordingly, the position of the washer 50 can be freely changed within the range in which the male screw side cooperation region 35 exists, so that the allowable range for the variation in the axial dimension of the fastened member 80 can be increased.
  • the bottom of the thread is left as much as possible, so that a decrease in the fastening force with the female screw body 90 hardly occurs.
  • the external thread body 10 of this 2nd embodiment illustrated the case where the external thread side cooperation area
  • region 35 was not provided in the cylindrical part 30a, by making the cross-sectional shape of the cylindrical part 30a substantially correspond with the external thread side cooperation area 35, The male screw side cooperation region 35 can be extended to the cylindrical portion 30a.
  • the cylindrical portion 30a itself can be eliminated.
  • FIG. 10 shows a modification of the second embodiment.
  • the second receiving portion 70 facing the fastened member 80 in the washer 50 is a tapered surface that protrudes toward the head 20 side of the male screw body 10 and is a “spring washer” as a whole.
  • the washer 50 can be elastically deformed.
  • the tightening pressure can be reduced by reducing the slope of the convex thread body side taper surface of the female thread body 90 (or making it flat), and increasing the angle of inclination of the washer side taper surface of the washer 90 to provide an angle difference.
  • the washer 50 can be elastically deformed.
  • the through-hole becomes small due to the stress, so that the washer-side contact portion can be pressed against the male screw-side contact portion, and the auxiliary engagement mechanism B can be strongly engaged.
  • FIG. 11 shows another modification of the second embodiment.
  • the male screw side contact part 120 in which the top of the screw thread is omitted in a concave shape when viewed from the axial direction. It is formed. More specifically, the male screw side contact portion 120 is configured such that the top of the screw thread is recessed in a V shape, and is formed at twelve locations in the circumferential direction at equal intervals.
  • the minimum distance (dent bottom) 35Y from the axial center of the male screw side contact portion 120 is set to be smaller than the maximum radius 30bX of the male screw portion 30b and larger than the minimum radius (valley bottom radius) 30bY of the male screw portion 30b.
  • the through hole 52 of the washer 50 assembled to the male screw body 10 also has a washer side contact that is convex inward in the radial direction so as to be similar to the male screw side cooperation region 35.
  • the contact portions 110 are formed at equal intervals in twelve places in the circumferential direction. As a result, the washer 50 and the male screw body 10 can be engaged in the circumferential direction.
  • the minimum distance 35Y from the axis of the male screw side contact part 120 is smaller than the minimum radius (valley bottom radius) 30bY of the male screw part 30b.
  • the present invention is not limited to this.
  • an axial groove deeper than the bottom of the thread can be formed, and this can be used as the male screw contact portion 120.
  • the minimum distance 35Y from the axis of the male screw side contact portion 120 is smaller than the minimum radius (valley bottom radius) of the male screw portion 30b.
  • the screw thread of the male screw part 30b is partially omitted including the valley bottom.
  • a washer-side contact portion 110 that protrudes radially inward is also formed in the through hole 52 of the washer 50, and the minimum distance from the axial center is the minimum radius of the male screw portion 30b (valley bottom radius, that is, the diameter of the valley). Make it smaller. As a result, it is possible to increase the engagement dimension in the circumferential direction between the washer-side contact portion 110 and the male screw-side contact portion 120.
  • the case where the inclined surface (tapered surface) is formed on the washer 50 and the female screw body 90 and the both are brought into contact with each other is illustrated.
  • the present invention is not limited to this.
  • a cylindrical surface is formed on both the washer 50 and the female screw body 90
  • a first receiving portion side unevenness 64 is formed on the cylindrical surface of the washer 50
  • a screw is formed on the cylindrical surface of the female screw body 90.
  • the case where the male screw body 90 has the head 20 is illustrated, but the present invention is not limited to this.
  • the head 20 is omitted, and a male screw portion 30b is formed therein, and a pair is formed from both sides.
  • the washers 50, 50 and the female screw bodies 90, 90, and fasten them so as to sandwich the fastened body 80. Even in this case, the male screw bodies 90, 90 arranged on both sides are prevented from rotating relative to the male screw body 10 in the loosening direction due to the presence of the washers 50, 50.
  • 13 and 14 can be applied to a method of fixing the pair of male screw bodies 90, 90 at an arbitrary place. Specifically, if the pair of washers 50 and 50 and the female screw bodies 90 and 90 are tightened without interposing the fastened member 80 between the pair of washers 50 and 50, they are fixed at an arbitrary place. It will be possible. Further, as an application, for example, as shown in FIG. 15, in addition to the first engagement mechanism A formed in the first receiving portion 60 of the washer 50, the second receiving portion 70 also has a second engagement with the female screw body 90. It is preferable to provide the mechanism C. As a result, by sandwiching one washer 50 between the pair of female screw bodies 90, 90, the pair of female screw bodies 90, 90 can be fixed to the male screw body 10 at an arbitrary location.
  • the case where the flat surface or the peripheral surface of the first receiving portion 60 of the washer 50 and the seat portion 92 of the female screw body 90 are brought into contact with each other in the circumferential direction is illustrated.
  • the present invention is not limited to this.
  • the arm that wraps around the polygonal circumferential surface of the female screw body 90 or the plane opposite to the seat portion 92 in the washer 50 is also preferable to form the second engagement mechanism C by forming 58 and engaging the arm 58 and the male screw body 90 in the circumferential direction.
  • this third embodiment is an application of the fastening structure of the screw body shown in FIG. 11 of the second embodiment, and description of members that are the same as or similar to these is omitted.
  • the fastening structure of the screw body is characterized in that the function of the washer (cooperating member) 50 is provided integrally with the female screw body 90 so that the independent washer (cooperating member) 50 can be omitted.
  • a female screw side cooperation region 91 a having a non-circular cross section when viewed from the axial direction is formed in a cylindrical portion 91 having a female screw portion 91 b that is screwed with the male screw portion 30 b.
  • This female screw body cooperation region 91a is provided on the opposite side of the female screw body 90 from the seat portion 92 so as to protrude in a ring shape in the axial direction, but may be provided on the seat portion 92 side and overlaps with the male screw portion 30b. You may form as follows.
  • female screw side contact portions 98 convex inward in the radial direction are formed on the inner peripheral surface of the cylindrical portion 91 at twelve locations in the circumferential direction at equal intervals.
  • the female screw side contact portion 98 can be engaged in the circumferential direction with the male screw side contact portion 120 formed to be recessed in the male screw portion 30 b of the male screw body 10.
  • the female screw side abutting portion 91a is provided on the opposite side of the seat portion 92 of the female screw body 90 in the axial direction so as to be thin and can be elastically deformed radially outward.
  • the female screw side contact portion 91a is elastically deformed outward and the circumferential engagement with the male screw side contact portion 120 is released. be able to. Therefore, as shown in FIG. 17, if the male screw body 10 and the female screw body 90 are urged in a direction to be tightened with a desired force, the male screw side contact portion 120 and the female screw side contact portion 91a are repeatedly engaged and released. Since the relative rotation can be allowed, the female screw body 90 can be fixed at an arbitrary position in the middle of the male screw portion.
  • the male screw side contact portion 120 of the male screw side cooperation region 35 extends linearly in the axial direction is mainly exemplified, but the present invention is not limited to this.
  • the male screw side contact portion 120 is formed so as to be spirally inclined with respect to the axial direction.
  • the spiral direction of the male screw side contact portion 120 is the same as the spiral direction of the thread of the male screw portion, and the lead is preferably set larger than the lead of the male screw portion.
  • the male screw body 10 is formed with a male screw side cooperation region 35 so as to overlap the male screw portion 30b.
  • the male screw side cooperation region 35 has a male screw side contact portion 120 in which a part of a regular circular shape formed along the apex of the screw thread is omitted in a concave shape.
  • the male screw side contact portion 120 is configured such that the top of the screw thread is recessed in a V shape, and the recess is formed at 48 locations at equal intervals in the circumferential direction. That is, the plurality of male screw side contact portions 120 are arranged with a phase pitch of 7.5 ° in the circumferential direction.
  • the minimum distance (dent bottom) 35Y from the axial center of the male screw side contact portion 120 is set to be smaller than the maximum radius 30bX of the male screw portion 30b and larger than the minimum radius (valley bottom radius) 30bY of the male screw portion 30b.
  • the radial height S of the recess of the male screw side contact part 120 (that is, from the top of the screw thread of the male screw part 30b).
  • the amount of omission of the dent inward in the radial direction) is preferably omitted with the upper limit being three-quarters of the thread height H, and more preferably with two-thirds of the thread height H being the upper limit.
  • the upper limit is one half of the thread height H.
  • it is set to one half of the height H of the thread.
  • the opening angle K of the V-shaped recess of the male screw side contact portion 120 is preferably 45 ° as an upper limit, more preferably 60 ° as an upper limit, and is set to 60 ° here.
  • the through hole 52 of the washer 50 assembled to the male screw body 10 has a similar shape to the male screw side cooperation region 35.
  • washer side contact portions 110 that are convex inward in the radial direction are formed at 48 locations at equal intervals in the circumferential direction.
  • the washer-type contact portion 110 has a high rigidity because it is a peak extending in the axial direction.
  • the washer-type contact portion 110 and the male screw side contact portion 120 can be engaged at least over the entire circumference, so that the circumferential engagement strength can be increased.
  • the washer-type contact portion 110 and the male screw side contact portion 120 can be engaged at least over the entire circumference, so that the circumferential engagement strength can be increased.
  • by securing engagement at a plurality of pitches (2.0 F or more) between the washer-type contact portion 110 and the male screw-side contact portion 120 stronger circumferential engagement can be realized.
  • the first receiving portion 60 of the washer 50 is formed with a washer-side tapered surface that is inclined in the radial direction.
  • the washer-side tapered surface is inclined so that the center side approaches the distal end side (the female screw body 90 side) of the male screw body 10 and has a convex conical shape.
  • the first receiving portion side unevenness 64 is formed on the washer side taper surface.
  • the female screw body 90 is formed with a seat portion 92 that faces the first receiving portion 60 of the washer 50.
  • a screw body side unevenness 94 is formed on the seat portion 92 of the female screw body 90.
  • the threaded body side seat portion 92 is formed with a threaded body side tapered surface inclined in the radial direction. Since the screw side taper surface is inclined so that the center side is away from the washer 50, a concave conical shape is obtained as a result.
  • FIGS. 29 to 31 it is possible to increase the axial dimension J of the washer-side contact portion 110 without increasing the total axial dimension of the engaging washer 50 and the female screw body 90.
  • the engagement strength in the circumferential direction of the engagement portion between the washer-type contact portion 110 and the male screw side contact portion 120 can be increased.
  • the male screw side contact portions 120 of the male screw body 10 are formed at 24 locations at equal intervals in the circumferential direction. That is, the plurality of male screw side contact portions 120 are arranged at a phase pitch of 15 °.
  • the minimum distance (dent bottom) 35Y from the axial center of the male screw side contact portion 120 is set to be smaller than the maximum radius 30bX of the male screw portion 30b and larger than the minimum radius (valley bottom radius) 30bY of the male screw portion 30b.
  • the radial height S of the recess of the male screw side contact part 120 (that is, from the top of the screw thread of the male screw part 30b).
  • the amount of omission of the dent inward in the radial direction) is preferably omitted with the upper limit being three-quarters of the thread height H, and more preferably with two-thirds of the thread height H being the upper limit. Omitted, and more preferably, the upper limit is one half of the thread height H.
  • the height S of the recess of the male screw side contact portion 120 is omitted within a range of 1 ⁇ 4 or more of the height H of the thread.
  • the opening angle K of the V-shaped recess of the male screw side contact portion 120 is preferably 45 ° as an upper limit, more preferably 60 ° as an upper limit, and is set to 60 ° here.
  • the maximum opening width T1 along the circumferential direction in the V shape of the recess is the distance T2 between the valleys along the circumferential direction of the adjacent V shape. Smaller than. As shown in FIG. 36, the maximum opening width T1 of the dent substantially matches the maximum base width T3 along the circumferential direction when the washer-side contact portion 110 is viewed from the axial direction.
  • the maximum shear distance in the circumferential direction of each washer-type contact portion 110 is the maximum base width T3 (that is, The maximum opening width T1), and the maximum shear distance in the circumferential direction of each male screw side contact portion 120 is the distance T2 between the valleys, and the relationship of T2> T3 is established.
  • the male screw side contact portion 120 is divided in the axial direction by superimposing the spiral strips of the male screw portion 30b, and the rigidity is likely to be lowered.
  • the washer-type contact portion 110 has a high rigidity because it is a peak extending in the axial direction. The difference in rigidity resulting from this shape feature can be compensated by the relationship of T2> T3.
  • the female screw body of the above embodiment is exemplified mainly for a general hex nut
  • the present invention is not limited to this, and a flanged nut, for example, can be adopted.
  • the engagement area with the cooperating member (washer) can be widened by the flange.

Landscapes

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

Abstract

Le corps fileté mâle selon la présente invention comprend une région d'assemblage côté corps fileté mâle présentant une section transversale de forme non circulaire en observant dans la direction axiale. Une rondelle (élément d'assemblage) comporte un trou traversant qui est non circulaire, et s'accouple avec la direction périphérique extérieure de la région d'assemblage côté corps fileté mâle. En outre, la rondelle est dotée d'un mécanisme d'accouplement qui s'accouple avec un corps fileté femelle dans la direction périphérique. Ainsi, il est possible d'empêcher de manière fiable une rotation d'un corps fileté dans une direction spécifique au moyen d'une structure simple.
PCT/JP2015/069500 2014-07-07 2015-07-07 Corps fileté mâle, élément d'assemblage, corps fileté femelle, et structure de fixation de corps filetés Ceased WO2016006598A1 (fr)

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JP2018089367A (ja) * 2016-11-30 2018-06-14 ストライカー・ユーロピアン・ホールディングス・Ｉ，リミテッド・ライアビリティ・カンパニー セレーション螺旋条を有する脊椎固定具
CN109973495A (zh) * 2018-04-07 2019-07-05 玉环胜友工具有限公司 类橄榄状对称双向锥形螺纹的螺栓与螺母连接结构
WO2019192574A1 (fr) * 2018-04-07 2019-10-10 玉环胜友工具有限公司 Structure de prise comportant un filetage externe à filetage conique bidirectionnel symétrique en forme d'haltère et un filetage classique
USD898196S1 (en) 2017-07-10 2020-10-06 Stryker European Holdings I, Llc Spinal fastener with serrated thread
JP2021092274A (ja) * 2019-12-10 2021-06-17 国立研究開発法人宇宙航空研究開発機構 締結構造、構造部材、締結具、移動体及び締結方法

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CN110131288B (zh) * 2019-06-19 2024-04-12 嘉兴光明科技股份有限公司 一种大型载重汽车轮毂用防盗螺母
JP7695650B2 (ja) * 2020-08-06 2025-06-19 株式会社進富 接合構造
KR102561319B1 (ko) * 2020-10-20 2023-07-27 (주)유닉코리아 풀림방지기능을 갖는 나사결합 어셈블리

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JPH0474714U (fr) * 1990-10-31 1992-06-30
US6010289A (en) * 1996-04-10 2000-01-04 Permanent Technologies, Inc. Locking nut, bolt and clip systems and assemblies
JP2003056528A (ja) * 2001-08-21 2003-02-26 Ito Denki Kk 支軸の固定装置、並びに、ローラ装置の固定装置
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Publication number Priority date Publication date Assignee Title
JP2018089367A (ja) * 2016-11-30 2018-06-14 ストライカー・ユーロピアン・ホールディングス・Ｉ，リミテッド・ライアビリティ・カンパニー セレーション螺旋条を有する脊椎固定具
JP2020014877A (ja) * 2016-11-30 2020-01-30 ストライカー・ユーロピアン・ホールディングス・Ｉ，リミテッド・ライアビリティ・カンパニー 脊椎修復システム
US11389205B2 (en) 2016-11-30 2022-07-19 Stryker European Operations Holdings Llc Spinal fastener with serrated thread
US12167871B2 (en) 2016-11-30 2024-12-17 Stryker European Operations Holdings Llc Spinal fastener with serrated thread
USD898196S1 (en) 2017-07-10 2020-10-06 Stryker European Holdings I, Llc Spinal fastener with serrated thread
USD926983S1 (en) 2017-07-10 2021-08-03 Stryker European Holdings I, Llc Spinal fastener with serrated thread
USD951454S1 (en) 2017-07-10 2022-05-10 Stryker European Operations Holdings Llc Spinal fastener with serrated thread
CN109973495A (zh) * 2018-04-07 2019-07-05 玉环胜友工具有限公司 类橄榄状对称双向锥形螺纹的螺栓与螺母连接结构
WO2019192574A1 (fr) * 2018-04-07 2019-10-10 玉环胜友工具有限公司 Structure de prise comportant un filetage externe à filetage conique bidirectionnel symétrique en forme d'haltère et un filetage classique
WO2019192555A1 (fr) * 2018-04-07 2019-10-10 玉环胜友工具有限公司 Structure de liaison de boulon et d'écrou de filetage définissant un contour en forme d'olive effilée de façon symétrique et bidirectionnelle
JP2021092274A (ja) * 2019-12-10 2021-06-17 国立研究開発法人宇宙航空研究開発機構 締結構造、構造部材、締結具、移動体及び締結方法
JP7296120B2 (ja) 2019-12-10 2023-06-22 国立研究開発法人宇宙航空研究開発機構 締結構造、構造部材、締結具、移動体及び締結方法

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JPWO2016006598A1 (ja) 2017-04-27
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JP6715455B2 (ja) 2020-07-01

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