WO2006008832A1 - Écrou résistant au desserrage - Google Patents

Écrou résistant au desserrage Download PDF

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Publication number
WO2006008832A1
WO2006008832A1 PCT/JP2004/010974 JP2004010974W WO2006008832A1 WO 2006008832 A1 WO2006008832 A1 WO 2006008832A1 JP 2004010974 W JP2004010974 W JP 2004010974W WO 2006008832 A1 WO2006008832 A1 WO 2006008832A1
Authority
WO
WIPO (PCT)
Prior art keywords
nut
axial
slits
female thread
opening
Prior art date
Application number
PCT/JP2004/010974
Other languages
English (en)
Inventor
Masato Nagawa
Hideki Noda
Original Assignee
Daiki Industries, Co., Ltd.
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 Daiki Industries, Co., Ltd. filed Critical Daiki Industries, Co., Ltd.
Priority to PCT/JP2004/010974 priority Critical patent/WO2006008832A1/fr
Publication of WO2006008832A1 publication Critical patent/WO2006008832A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B39/00—Locking of screws, bolts or nuts
    • F16B39/22—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening
    • F16B39/28—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening by special members on, or shape of, the nut or bolt
    • F16B39/284—Locking by means of elastic deformation
    • F16B39/286—Locking by means of elastic deformation caused by saw cuts

Definitions

  • the present invention relates to a loosening-proof nut, which serves to tighten a subject by being screwed on the male thread of a bolt or the like and can also prevent reduction of the tightening force even in case when the subject or bolt experiences external generated vibrations or the like.
  • a combination of a bolt and a nut is used for tightening various parts of transport means such as vehicles and airplanes, various industrial machines and apparatuses, transport pipelines and electric power transmission facilities.
  • No. 2002-39143 see Figs.l, 2 and 3(b)) has slits formed from the opposite sides at its vertically intermediate position.
  • the nuts according to the patent Literatures 1 to 3 each have a slanted tightening surface so as to form a projecting part, in which a slit is formed. Therefore, these nuts also pose problems that their manufacture is somewhat difficult and is difficult in manufacture by using a JIS standard nut.
  • the nut disclosed in the Literature 4 although the nut has the slits formed from the opposite sides, these sides are in lower parts in the tightening direction. Besides, these lower parts have protuberances.
  • the nut dictates considerable cost of manufacture.
  • the lower part or part formed by the slit or slits are pushingly bent. This means that a sufficient force is required for finally tightening the nut.
  • a great load is applied to a lower part of the bolt, on which the nut is screwed.
  • the tightening surface is readily subject to scars and scratches due to partial load exerted thereto. Therefore, a washer is required to avoid scars and scratches, which may otherwise formed in the subject.
  • no loosening-proof action is obtainable unless the nut is tightened against the subject.
  • the present invention was made in view of the above background, and it has an object of providing a loosening-proof nut, which does not apply any eccentric load to the bolt, and is capable of being readilymanufacturedwith good load balance to the bolt.
  • a loosening-proof nut comprising a nut body having a central female thread with a nominal diameter d, the nut body also having two or more slits formed such as to be symmetrical with respect to the axis of the nut, radially penetrate the female thread from the outer periphery of the nut and be located at an axial position on the upper side of the axial center position of the nut body, the slits defining push parts, which are bent downward by causing plastic deformation.
  • the slits consist of a first and a second slit symmetrical with respect to the axis of the nut
  • the push parts consist of a first and a second push part defined in an upper part of the nut body by the first and second slit
  • the distance b between the bottoms of the first and second slit is in a range of 0.15 to 0.8 times the nominal diameter d.
  • the first and second slits are formed at a position above the vertical center of the nut body.
  • the first and second push parts which are defined in an upper part of the nut body by the first and second slits, plastically deformed and bent downward.
  • the height h of the nut body is at least 0.5 times the nominal diameter d
  • the bottom width of the first and second slits is 0.05 to 0.2 times the nominal diameter d
  • the thickness a of the first and second push parts is 0.1 to 0.3 times the nominal diameter d.
  • the width s of the tip of the first and second push part is in a range of 0 to 0.5 times (preferably, o or a range of 0 to 0.2 times) the bottomwidth g of the first and second slits.
  • the first and second slits are at an angle between 70 and 90 degrees with respect to the axis of the nut body and are formed substantially symmetricallywith respect to the axis of the female screw. In case where the first and second slits are at an angle of 90 degrees with respect to the axis of the nut body, the manufacture can be facilitated very much. In case of a slit angle between 70 and 90 degrees, it is possible to adjust the reaction forces of the first and second push parts by appropriately selecting the angle.
  • the slits which are at an angle between 70 and 90 degrees may be slanted either upward or downward.
  • the upper part of the nut body inclusive of the first and second push parts is circular in plan view shape.
  • the first and second push parts are free from being hooked by any tool such as a spanner, and are not deformed during work.
  • the nut body part which is located below the part which is circular in plan view usually hexagonal in plan view shape, but it may be quadrangular, octagonal, circular, etc. in pan view shape as well.
  • the dimensions according to the third to sixth aspects of the present invention are applicable to the height h of the nut body, bottom width g of the slits and the height h of the push parts.
  • a nut having an internal female thread, a first opening fromwhich a male thread to be screwed is inserted, and a second opening, from which the inserted male thread gets out; wherein the nut comprises at least a pair of slits formed at an axial position closer to the second opening and such as to be symmetrical with respect to the axis of the nut and to radially partly penetrate the female thread from the outer periphery of the nut, a first axial part defined on the first opening side and a second axial part defined on the second opening side bounded by the pair of slits, and the female thread parts of the first and second axial parts have the same shape parameter, and the direction of the surface, inwhich the female thread part in the second axial part is formed, is deviated from the axial direction.
  • a nut having an internal female thread, a first opening from which a male thread to be screwed is inserted, and a second opening, from which the inserted male thread gets out; wherein the nut comprises at least a pair of slits formed at an axial position closer to the second opening and such as to be symmetrical with respect to the axis of the nut and to radially partly penetrate the female thread from the outer periphery of the nut, a first axial part defined on the first opening side and a second axial part defined on the second opening side bounded by the pair of slits, and the female thread parts of the first and second axial parts have the same shape parameter, andthe direction of the surface, inwhichthe female thread part in the second axial part is formed, is deviated from the axial direction by causing plastic deformation of the second axial part.
  • a nut having an internal female thread, a first opening fromwhich a male thread to be screwed is inserted, and a second opening, from which the inserted male thread gets out; wherein the nut comprises at least a pair of slits formed at an axial position closer to the second opening and such as to be symmetrical with respect to the axis of the nut and to radially partly penetrate the female thread from the outer periphery of the nut, a first axial part defined on the first opening side and a second axial part defined on the second opening side bounded by the pair of slits, and the female thread parts of the first and second axial parts have the same shape parameter, and the width of the slit is increased in the axial direction by causing plastic deformation of the second axial part.
  • a nut having an internal female thread, a first opening fromwhich a male thread to be screwed is inserted, and a second opening, from which the inserted male thread gets out; wherein the nut comprises at least a pair of slits formed at an axial position closer to the second opening and such as to be symmetrical with respect to the axis of the nut and to radially partly penetrate the female thread from the outer periphery of the nut, a first axial part defined on the first opening side and a second axial part defined on the second opening side bounded by the pair of slits, the female thread parts of the first and second axial parts have the same shape parameter, and the directionof the surface, inwhich the female thread part in the second axial part is formed, is deviated from the axial direction, and the maximum outer diameter of the second axial part is smallerthan theminimumouter diameter of the first axial part.
  • a nut having an internal female thread, a first opening from which a male thread to be screwed is inserted, and a second opening, fromwhich the inserted male thread gets out; wherein the nut comprises at least a pair of slits formed at an axial position closer to the second opening and such as to be symmetrical with respect to the axis of the nut and to radially partly penetrate the female thread from the outer periphery of the nut, a first axial part defined on the first opening side and a second axial part defined on the second opening side bounded by the pair of slits, and the female thread parts of the first and second axial parts have the same shape parameter, the second axial part being plastically deformed to increase the width of the slits toward the axis of the nut; and the maximum outer diameter of the second axial part is set to be smaller than the minimum outer diameter of the first axial part.
  • the outer periphery of the second axial part is circular in shape.
  • the first and second axial part have substantially the same shape.
  • the female thread part formation surface direction of the second axial part is set to be outward from the axis of the nut.
  • As the pair of slits a plurality of slit pairs are formed at predetermined positions uniformly subtending the circumference.
  • the maximum outer diameter of the second axial part is smaller than theminimumouter diameter of the first axial part.
  • the outer periphery of the second axial part is circular in shape.
  • Fig. 1 is a sectional view showing an embodiment of the loosening-proof nut according to the present invention
  • Fig. 2 is a plan view showing the same loosening-proof nut
  • Fig. 3 is a side view showing a method of manufacturing the same loosening-proof nut
  • Figs. 4(A) and 4(B) are a partial plan view and a sectional view showing a loosening-proof nut showing a second embodiment of the loosening-proof nut according to the present invention
  • Fig. 1 is a sectional view showing an embodiment of the loosening-proof nut according to the present invention
  • FIG. 2 is a plan view showing the same loosening-proof nut, Fig.
  • FIG. 3 is a side view showing a method of manufacturing the same loosening-proof nut
  • Figs.4(A) and 4(B) are a partial plan view and a sectional view showing a loosening-proof nut showing a second embodiment of the loosening-proof nut according to the present invention.
  • the first embodiment of the loosening-proof nut 10 comprises a nut body 11 with a central female thread 12 having a nominal diameter d.
  • nominal diameter is used for representing the nut size in JIS or like standards, and is substantially identical with the valley bottom diameter of the female thread 12.
  • the height h of the nut body 11 is more than 0.5 times, i.e., about 0.75 to 1.1 times, the nominal diameter d. With this height h, the loosening-proof nut 10 provides a sufficient tightening force.
  • the female thread 12 may be of various pitch sizes, such as thick, medium and thin, and the present invention is applicable to any pitch size.
  • the loosening-proof nut 10 When the height h of the loosening-proof nut 10 is small, i.e., smaller than the above range, the loosening-proof nut 10 is impractical due to low values of the tightening load and the above loosening-proof load.
  • the height h of the loosening-proof nut 10, on the other hand, may be increased since the performance is not affected, although space problems may be encountered.
  • the opposite sides of the nut body 11 are formed with a first and a second diametrically symmetrical slit 13 and 14, thus forming a first and a second corresponding push part (or loosening-proof part) 15 and 16 of the nut body 11.
  • the first and second slits 13 and 14 have to be formed in parts of the female thread 12.
  • the first and second slits 13 and 14 are formed symmetrically with respect to and at right angles (90 degrees) to the axis of the female thread 12.
  • the first and second slits 13 and 14 may also be formed to be at an angle between 70 and 90 degrees to the axis of the female screw 2.
  • the nut body 11 is formed on the opposite sides thereof with two slits 13 and 14 on the opposite side, it is also possible to form three 120 degrees spaced-apart slits reaching the inner female thread 12.
  • the distance b between the bottoms of the first and second slits 13 and 14 is 0.15 to 0.8 times (preferably 0.3 to 0.7 times) the nominal diameter d.
  • the bottom width of the first and second slits is 0.05 to 0.2 times the nominal diameter d (preferably, 0.08 to 0.15 times) .
  • the thickness a of the first and second push parts, which are formed in an upper part of the nut body 11 by the first and second slits 13 and 14, is 0.1 to 0.3 times (preferably 0.15 to 0.25 times) the nominal diameter d.
  • the tip width (or clearance) is of the first and second push parts 15 and 16 is in a range of 0 to 0.5 times (preferably less than 0.3 times) the bottom width of the first and second slits 13 and 14. Under these dimensional conditions, the first and secondpush parts 15 and 16 can be readily formedby bending. Specifically, for the bending formation, as shown in Fig. 3, the nut body 11 with the first and second slits 13 and 14 formed therein is set on a die 17, and its part defined by the first and second slits 13 and 14 are pushed down with a ponch 20 having symmetrical downward protuberances 18 and 19.
  • the parts defined by the first and second slits 13 and 14 are pushed down until their tips are brought into contact with the bottom surfaces of the first and second sits 13 and 14.
  • the push parts undergo plastic deformation to become the first and second push parts 15 and 16.
  • the tip width s is increased due to plastic deformation.
  • first and second push parts 15 and 16 shown in Fig. 2 are bent downward from their parts corresponding to the bottom of the first and second slits 13 and 14.
  • the first and second push parts 15 and 16 are formed with partial female threads 21 and 22, which are continuous with the female thread of the nut body 11 but are bent downward from their central part.
  • the distance b between the bottoms of the first and second slits 13 and 14 is set to 0.15 to 0.8 times (preferably 0.3 to 0.7 times) the nominal diameter d.
  • the distance b is larger than this range, no region for the formation of the partial threads 21 and 22 is provided.
  • the distance d is smaller than this range, on the other hand, the mechanical strength of parts 27 and 28 between the bottoms of the first ad second slits 13 and 14 is reduced.
  • the bottom width (or bottom height) g of the first and second slits 13 and 14 is set to be 0.05 to 0.2 ties (preferably 0.08 to 0.15 times) the nominal diameter d. This is so because when the bottom width g is less than the nominal diameter d, no bending margin of the first and second push parts 15 and 16 is provided. When the bottom with g exceeds 0.2 times, on the other hand, the first and second push parts 15 and 16 are excessively bent, and also the regions of the partial female threads 21 and 22 and the female thread 12 are reduced.
  • the thickness a of the first and second push parts 15 and 16 is set to be 0.1 to 0.3 times (preferably 0.15 to 0.25 times) the nominal diameter d. This is so because when the thickness a of the first and second push parts 15 and 16 is less than this range, it is impossible to produce a sufficient loosening-proof load. When the thickness a exceeds the range, on the other hand, an excessive loosening-proof load is produced. Further, the necessary height of the loosening-proof nut is increased, which is undesired from the standpoint of economy. Labeled c in Fig. 2 is the depth of cut with respect to the female screw 12.
  • the loosening-proof nut 10 When the bolt is screwed through the loosening-proof nut 10, the downwardly bent first and second push parts 15 and 16 are raised. Thus, the maximum load is produced in the stem parts 23 to 26 of the first and second push parts 15 and 16. Thus, the loosening-proof nut 10 can be used repeatedly so long in a range that these parts do not undergo plastic deformation.
  • the load for providing the loosening-proof action with respect to the bolt is produced in the part, in which the loosening-proof threads 21 and 22 are screwed through the bolt.
  • the loosening-proof nut 10 when a predetermined bolt is screwed through the loosening-proof nut 10 in the state that the tips of the first and second push parts 15 and 16 of the nut 10 are pushed down (that is, with slit width s of zero or nearly zero), for the first time the first and second push parts 15 and 16 are raised with plastic deformation, and in the state that the screwed state of the bolt is released, the first and second push parts 15 and 16 are slightly raised to increase the slit width s. For the second and further times, however, the first and second push parts 15 and 16 undergo plastic deformation, and thus the loosening-proof nut 10 can be used repeatedly.
  • the screwing of the bolt through the loosening-proof nut 10 requires a predetermined preparing torque.
  • This load i.e., loosening-proof load
  • the height of the loosening-roof nut 10 and the dimensions of the first and second slits 13 and 14 and the first and second push part 15 and 16 satisfy the above dimensions and that the area Sl of the partial female threads 21 and 22 is 0.04 to 0.3 times (preferably 0.08 to 0.25 times) the substantial female thread area ( TCdh) of the loosening-proof nut 10.
  • Figs. 4(A) and 4(B) show a second embodiment of loosening-proof nut 30 according to the present invention, which will now be described.
  • This nut 30 is different from the loosening-proof nut 10 described above in that an upper part 32 of the nut body 31 is circular in plan view shape.
  • the upper part 32 includes the periphery of the first and second push parts 33 and 34, and in this embodiment it also includes lower parts of the first and second slits 35 and 36.
  • the loosening-proof nut 30 is the same as the loosening-proof nut 10, and are hence not described while providing like reference numerals.
  • the surface to be in contact with the subject i.e., the bottom surface of each of the nut bodies 11 or 31
  • the surface to be in contact with the subject is formed as a surface normal to the axis of each of the nut bodies 11 and 31.
  • the nut body has the slits formed symmetrically with respect to its axis such as to reach the female thread, no eccentric load is applied to the bolt.
  • the female thread in a lower part of the nut body has an action of tightening the subject, the partial female threads formed in push parts in the upper part of the nut body provide a loosening-proof load to the bolt, and these actions are in opposite directions.
  • no such great load as applied when the two actions are otherwise both applied to the bolt is generated. It is thus possible to enhance the mechanical strength of the bolt itself even in such extreme state as super-low or super-high temperature state.
  • the loosening-proof nut inwhich the slits consist of a first and a second slit symmetrical with respect to the axis of the nut, the push parts consist of a first and a second push part defined in an upper part of the nut body by the first and second slit, and the distance b between the bottoms of the first and second slit is in a range of 0.15 to 0.8 times the nominal diameter d is easy to be manufactured.
  • the height h of the nut body is at least 0.5 times the nominal diameter d
  • the bottom width of the first and second slits is 0.05 to 0.2 times the nominal diameter d
  • the thickness a of the first and second push parts is 0.1 to 0.3 times the nominal diameter d
  • the loosening-proof nut has a structure in which the width s of the tip of the first and second push part is in a range of 0 to 0.5 times the bottom width g of the first and second slits.
  • the press process for the push parts can be readily carried out by applying an adequate loosening-proof force to the partial female threads formed in the push parts.
  • the width s at the tip of the ' first and second push parts is preset to zero or nearly zero with respect to the bottom width g of the first and second slits, the first and second push parts can be readily pushingly bent in the press process.
  • the loosening-proof nut has structure in which the first and second slits are at an angle between 70 and 90 degrees with respect to the axis of the nut body and are formed substantially symmetrically with respect to the axis of the female screw. In the case where the first and second slit are at an angle of 90 degrees with respect to the nut body axis, the manufacture can be extremely facilitated. In the case where the slit angle is between 70 and 90 degrees, it is possible to adjust the degree of the push bending of the first and second push parts and provide a best loosening-proof nut.
  • the loosening-proof nut has a structure in which the upper part of the nut body inclusive of the first and second push parts is circular in plan view shape. Thus, the first and second push parts are free from being hooked by any tool such as a spanner, and are not deformed during work.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bolts, Nuts, And Washers (AREA)

Abstract

L’invention concerne un corps d’écrou 11 ayant un filet femelle central 12 qui possède également une première et une deuxième fente 13 et 14 formées de façon à pénétrer partiellement dans le filet femelle central depuis les côtés opposés. La distance b entre les parties inférieures des première et deuxième fentes 13 et 14 est comprise entre 0,15 et 0,8 fois le diamètre nominal d. Une première et une deuxième partie de poussée 15 et 16 qui sont formées dans la partie supérieure du corps d’écrou 11 par les première et deuxième fentes 13 et 14 pliées vers le bas par déformation plastique.
PCT/JP2004/010974 2004-07-22 2004-07-22 Écrou résistant au desserrage WO2006008832A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2004/010974 WO2006008832A1 (fr) 2004-07-22 2004-07-22 Écrou résistant au desserrage

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2004/010974 WO2006008832A1 (fr) 2004-07-22 2004-07-22 Écrou résistant au desserrage

Publications (1)

Publication Number Publication Date
WO2006008832A1 true WO2006008832A1 (fr) 2006-01-26

Family

ID=35784967

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2004/010974 WO2006008832A1 (fr) 2004-07-22 2004-07-22 Écrou résistant au desserrage

Country Status (1)

Country Link
WO (1) WO2006008832A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52131565U (fr) * 1976-04-02 1977-10-06
JPS5730410U (fr) * 1980-07-28 1982-02-17
JPS5940011A (ja) * 1982-08-31 1984-03-05 岩田ボ−ルト工業株式会社 緩み止めダブルナツト
JPS62181713U (fr) * 1986-05-10 1987-11-18
JPH0685923U (ja) * 1992-10-13 1994-12-13 株式会社白河捻子製作所 緩み止めナット

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52131565U (fr) * 1976-04-02 1977-10-06
JPS5730410U (fr) * 1980-07-28 1982-02-17
JPS5940011A (ja) * 1982-08-31 1984-03-05 岩田ボ−ルト工業株式会社 緩み止めダブルナツト
JPS62181713U (fr) * 1986-05-10 1987-11-18
JPH0685923U (ja) * 1992-10-13 1994-12-13 株式会社白河捻子製作所 緩み止めナット

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