EP2646697A2 - Écrou autobloquant - Google Patents

Écrou autobloquant

Info

Publication number
EP2646697A2
EP2646697A2 EP11833605.6A EP11833605A EP2646697A2 EP 2646697 A2 EP2646697 A2 EP 2646697A2 EP 11833605 A EP11833605 A EP 11833605A EP 2646697 A2 EP2646697 A2 EP 2646697A2
Authority
EP
European Patent Office
Prior art keywords
self
areas
locking nut
core hole
nut
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.)
Withdrawn
Application number
EP11833605.6A
Other languages
German (de)
English (en)
Inventor
Frank-Uwe Diener
Wolfgang Giraud
Siegfried OBERNDÖRFER
Thorsten Schraer
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.)
Ruia Global Fasteners AG
Original Assignee
Ruia Global Fasteners AG
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 Ruia Global Fasteners AG filed Critical Ruia Global Fasteners AG
Publication of EP2646697A2 publication Critical patent/EP2646697A2/fr
Withdrawn legal-status Critical Current

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
    • 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 self-locking nut, which is also referred to as a "clamping nut”, with a core hole and thread grooves.
  • this object is achieved by a self-locking nut or clamping nut which has a core hole with a reduced inside diameter in one or more areas.
  • the areas between the thread grooves in one or more parts of the internal thread can not be flattened, but can be formed in a pointed ridge which protrudes beyond the remaining internal thread.
  • Such a clamping nut according to the invention has the following advantages: The manufacturing costs are lower and can correspond to the production costs of a standard nut without clamping or self-locking effect, since no additional material and no additional processing step is necessary to achieve the clamping effect.
  • the clamping effect can be co-produced according to the invention during cold working or during thread cutting.
  • Nuts according to the invention weigh less and have a lower overall height than tapered clamping nuts. As a result, they do not require so long screws or bolts and no extra space in the application.
  • the clamping nuts according to the invention also have a much better clamping action, since the clamping does not act diagonally, and finally the self-locking nuts according to the invention have little or no tendency to seizure.
  • the areas of reduced core hole inner diameter each extend over only a small portion of the circumference of the core hole of preferably 10 to 15 degrees. In this way, a seizure of the screw connection is prevented, although still a sufficiently high clamping effect can be achieved.
  • the areas with reduced core hole diameter only in the three to four last, that is remote from the screw side of the nut threads of the internal thread. The nut then only clamps when it is screwed almost completely onto the screw or the bolt.
  • the areas of reduced core hole diameter may preferably be formed by flat portions on the inner diameter of the core hole.
  • the nut according to the invention is particularly easy to produce, since the core hole is usually produced today by pressing and only at the remote from the workpiece end of the nut a ram with corresponding flats must be used. Apart from the one-time conversion of the tool, so the stamp, then incurred no further costs in the production of the mother of the invention.
  • the areas formed as a sharp ridge extend only over a small portion of the circumference of the internal thread, since this can further reduce the tendency to seizure.
  • the formed as a sharp ridge areas extend only between the three to four last, that is remote from the workpiece side of the nut thread furrows of the internal thread. In this way, the mother only clamps when it has been screwed sufficiently far on the bolt.
  • Figure 1 is a sectional view of a clamping nut according to the invention.
  • FIG. 2 shows the clamping nut of FIG. 1 from above
  • Figure 4 shows the clamping nut of Figure 1 from above with screwed and cut at height of the nut nut;
  • FIG. 5 shows the illustration of FIG. 3 with the bolt inserted
  • FIG. 6 shows the detail X of FIG. 5.
  • Figure 1 shows a clamping nut according to the invention or self-locking nut 10 from the side in a sectional view.
  • the internal thread 12 is not shown in greater detail in accordance with the usual drawing standards. Shown are those areas 14 in which the core hole diameter is reduced, or increased burrs are provided between the thread grooves. As shown, these areas 14 extend over almost half the length of the internal thread of the nut 10, these are usually three to four threads.
  • FIG. 2 shows the mother of Figure 1 from above, again the internal thread 12 and the areas 14 can be seen with reduced core hole diameter or raised burrs between the thread grooves.
  • FIG. 2 it can be seen very clearly that in the present embodiment there are three areas 14 with reduced core hole diameters or raised burrs between the thread grooves, which are distributed equally spaced over the thread turn, so that the distance between the individual areas 14 is 120 degrees.
  • FIG. 3 shows the nut of FIG. 1 partially cut along the line A-A of FIG. 4 with a detailed representation of the internal thread 12.
  • the area 14 on the top right in the image can already be seen very well with the differently shaped thread according to the invention
  • a conventional internal thread 12 is shown in the lower part of the illustrated nut 10. This consists, as usual, of V-shaped grooves 16 between which flattened portions 18 extend, which abut geo-metrically on the lateral surface of a cylinder with the core hole diameter.
  • flanks 19 of the V-shaped grooves 16 are extended and meet in a pointed ridge 20, which therefore projects into an imaginary cylinder with the core hole diameter.
  • Figure 4 shows the clamping nut according to the invention or self-locking nut 10, in which case a bolt 100 is screwed, which is shown cut at the height of the upper end of the nut 10. Again, the areas 14 with the reduced core hole diameter are clearly visible again. Here is also very well recognizable, as in the area 14, the core hole diameter of bolt 100 and nut 10 coincide, whereby the present invention desired clamping effect is brought about.
  • FIG. 5 likewise shows the combination of nut 10 and bolt 100 shown in FIG. 4, wherein the nut 10 is again shown partially cut along the lines A-A of FIG. 4 as in FIG.
  • the bolt 100 is not shown cut for clarity, so you can see the external thread 102 of the bolt well.
  • the bolt 100 may be commercially available and comply with the usual technical standards.
  • the inventive meshing of the external thread 102 of the commercial bolt 100 with the inventively modified region 14 of the internal thread 12 of the nut 10 is shown in more detail than detail X in Figure 6.
  • the internal thread 102 of the bolt 100 is shown cut to better illustrate the clamping action of the invention.
  • the region of the internal thread 12 of the nut 10 is shown, which is normal, that is formed according to the prior art, so that the difference to the inventive design of regions 14 of the internal thread 12 emerges even more clearly.
  • the lower two threads of the internal thread 12 of the nut 10 in Fig. 6 are normally formed according to the prior art, while the upper three threads shown in Fig. 6 have a reduced core hole diameter.
  • the flanks 19 of the V-shaped thread grooves 16 normally terminate in a flattened region 18 which separates the individual thread grooves 16 and whose surface corresponds to the surface area of a cylinder having the standard core hole diameter. In this way, over the entire length of thread required for low-friction screwing of the bolt 100 in the nut 10 game 22 is guaranteed. Only when a biasing force between bolt 100 and nut 10 acts normally flanks 19 of the nut thread against the opposite flanks of the bolt are pressed in not self-locking nuts, and by the thereby triggered friction holds the screw.
  • the plateau-like region 18 is missing between the individual threads 16 of the internal thread 12 of the nut 10. Instead, the flanks 19 of the individual thread grooves 16 in this region 14 pass over only a very large part small radius into each other, whereby protruding ridges 20 are formed between the thread grooves 16.
  • FIG. 6 shows the theoretical geometric relationships.
  • the black area of the ridges 20 shown is actually not present, but in this area the ridges 20 are elastically deformed by the contact pressure to the valley bottom of the grooves 116 of the bolt 100.
  • the burrs 20 are actually somewhat “flattened” while penetrating into the bottom of the grooves 116 of the external thread of the bolt 100 at the same time. Since this effect occurs from several sides simultaneously, a clamping of the screw and thus a self-assurance is achieved, regardless of whether a biasing force has already occurred during screwing, or not.
  • two or more, preferably three uniformly spaced regions 14 are provided according to the invention over the circumference of the internal thread 12 of the nut 10.
  • the regions 14 can be manufactured in different ways:
  • nuts are usually manufactured today by cold forming, stamping punches with the core hole diameter from above and below, and then cutting, rolling or rolling the thread.
  • the punch diameter can be selected to be somewhat smaller, since with a chipless production of the internal thread 12 of the nut 10, the material displaced by the formation of the thread grooves 16 is displaced into the regions 18 between the thread grooves.
  • the regions 14 can now be produced simply by grinding or hollowing out these regions on the stamp which acts on the mother from above. In this way, either a secant-shaped, ie flat region 14 can be produced, or what is still preferred according to the invention and also shown here, an inwardly curved region 14. This inward curvature is particularly preferred in order to seize the thread in the clamping state avoid.
  • the curvature is defined with a large radius from the outside.
  • the regions 14 can be produced in non-cutting production of the internal thread 12 by making the thread grooves 16 of the internal thread 12 deeper and / or wider in the region 14, whereby more material is deformed and correspondingly higher burrs are raised between the individual threads become.
  • the production of a clamping nut according to the invention is not complicated or complicated than the production of a commercial-usual mother without clamping action. Only the manufacturing tools, so either the punch for the production of the core hole or the tools for thread rolling or thread rolling, must be performed once differently.

Landscapes

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

Abstract

L'invention concerne un écrou autobloquant (10) comportant un filet intérieur (12) et un avant-trou présentant une ou plusieurs zones (14) ayant un diamètre intérieur réduit.
EP11833605.6A 2010-11-29 2011-11-24 Écrou autobloquant Withdrawn EP2646697A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202010015819U DE202010015819U1 (de) 2010-11-29 2010-11-29 Selbstsichernde Mutter
PCT/DE2011/050050 WO2012076004A2 (fr) 2010-11-29 2011-11-24 Écrou autobloquant

Publications (1)

Publication Number Publication Date
EP2646697A2 true EP2646697A2 (fr) 2013-10-09

Family

ID=43495887

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11833605.6A Withdrawn EP2646697A2 (fr) 2010-11-29 2011-11-24 Écrou autobloquant

Country Status (11)

Country Link
US (1) US20130236265A1 (fr)
EP (1) EP2646697A2 (fr)
JP (1) JP2013543963A (fr)
KR (1) KR20130140751A (fr)
CN (1) CN103348147A (fr)
AU (1) AU2011341143A1 (fr)
BR (1) BR112013011974A2 (fr)
CA (1) CA2819179A1 (fr)
DE (1) DE202010015819U1 (fr)
MX (1) MX2013005993A (fr)
WO (1) WO2012076004A2 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011100247A1 (de) 2011-04-26 2012-10-31 Oswald Gleixner-Hauler Verbindungssystem
US10061411B2 (en) * 2016-08-19 2018-08-28 Microsoft Technology Licensing, Llc Dual-function switch for stylus tail eraser
CN108105247A (zh) * 2016-11-25 2018-06-01 诠丰精密工具股份有限公司 具内螺纹件及内螺纹成型工具
US11940000B2 (en) * 2019-06-17 2024-03-26 Volvo Car Corporation Partially-threaded projection weld nut
KR20210034199A (ko) 2019-09-20 2021-03-30 현대중공업 주식회사 일점계류 셔틀탱커

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2190174A (en) * 1938-08-06 1940-02-13 Burdsall & Ward Co Lock nut
EP2224143A1 (fr) * 2009-02-26 2010-09-01 PAGE Profilverbindungstechnik GmbH Ecrou, raccordement de vis, connexion de profilé, ainsi que procédé de fabrication d'un écrou

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US793824A (en) * 1904-12-15 1905-07-04 American Iron And Steel Mfg Co Inc Bolt and nut lock.
US1903921A (en) * 1932-02-08 1933-04-18 Ernest L Rupf Lock nut and method of manufacture
US2373473A (en) * 1944-02-15 1945-04-10 Edgar R Henningsen Lock nut
US2452192A (en) * 1944-05-10 1948-10-26 Richard T Hosking Lock nut
BE482871A (fr) * 1946-03-01
US2754871A (en) * 1952-09-04 1956-07-17 Stoll Albert Self-locking nut having a radially deformed thread portion and method for the production of the same
DE1007566B (de) * 1954-12-06 1957-05-02 Albert Stoll Selbstsichernde Schraubenmutter
US2983180A (en) * 1957-08-07 1961-05-09 Illinois Tool Works Die nut having an aperture shaped as a regular polygon
US2923339A (en) * 1957-11-25 1960-02-02 Harold J Skidmore Lock nut having external projections deformed radially inwardly
US3381733A (en) * 1966-07-01 1968-05-07 Glenn W. Stanwick Thread form
US3426820A (en) * 1967-10-05 1969-02-11 Res Eng & Mfg High friction screw
FR1549506A (fr) * 1967-10-31 1968-12-13
US3520344A (en) * 1968-07-17 1970-07-14 Eric G Gabbey Self-locking screw thread
US3841371A (en) * 1968-07-30 1974-10-15 Microdot Inc Lock nut
US3664400A (en) * 1970-03-02 1972-05-23 George W Moore Inc Locking set screw
US4024899A (en) * 1976-03-09 1977-05-24 Stewart Mary L W Lock nut and bolt construction
EP0004541A1 (fr) * 1978-02-17 1979-10-17 B E L I P A R, Société Anonyme Vis, notamment vis autotaraudeuse et machine à laminer les filets pour sa fabrication
US4826377A (en) * 1981-04-27 1989-05-02 Holmes Horace D Self-locking fastener and tool for making same
GB2156025A (en) * 1984-03-14 1985-10-02 Avdel Ltd Self locking blind fasteners
CN87105389A (zh) * 1986-07-31 1988-02-24 帕特里克·耶尔弗顿·威廉斯 自锁螺母
DE4031602A1 (de) * 1990-10-05 1992-04-09 Hartmut Flaig Hammermutter
US5342096A (en) * 1991-11-15 1994-08-30 General Signal Corporation Connector with captive sealing ring
US5672037A (en) * 1994-11-01 1997-09-30 Iwata Bolt Kabushiki Kaisha Loosening and dislodging preventing screw
DE19708286B4 (de) * 1997-02-28 2006-01-19 Nedschroef Plettenberg Gmbh Blechteil
DE10238055B4 (de) * 2002-08-20 2004-10-28 Ejot Gmbh & Co. Kg Mit selbstklemmendem Gewinde versehene Schraube
JP5005909B2 (ja) * 2005-11-18 2012-08-22 勝行 戸津 ねじ具の緩み止め締結具及びその製造方法
EP2211064A1 (fr) * 2009-01-27 2010-07-28 Siemens Aktiengesellschaft Ecrou à fermeture automatique

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2190174A (en) * 1938-08-06 1940-02-13 Burdsall & Ward Co Lock nut
EP2224143A1 (fr) * 2009-02-26 2010-09-01 PAGE Profilverbindungstechnik GmbH Ecrou, raccordement de vis, connexion de profilé, ainsi que procédé de fabrication d'un écrou

Also Published As

Publication number Publication date
MX2013005993A (es) 2013-07-22
WO2012076004A2 (fr) 2012-06-14
JP2013543963A (ja) 2013-12-09
DE202010015819U1 (de) 2011-01-20
US20130236265A1 (en) 2013-09-12
CN103348147A (zh) 2013-10-09
WO2012076004A3 (fr) 2012-08-02
CA2819179A1 (fr) 2012-06-14
AU2011341143A1 (en) 2013-05-02
KR20130140751A (ko) 2013-12-24
BR112013011974A2 (pt) 2016-08-30

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