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
  • F16B39/02—Locking of screws, bolts or nuts in which the locking takes place after screwing down
  • F16B39/12—Locking of screws, bolts or nuts in which the locking takes place after screwing down by means of locknuts
  • F16B39/126—Locking of screws, bolts or nuts in which the locking takes place after screwing down by means of locknuts causing radial forces on the bolt-shaft
  • F16B39/128—Locking of screws, bolts or nuts in which the locking takes place after screwing down by means of locknuts causing radial forces on the bolt-shaft by means of eccentrical or spiral interengaging parts

Definitions

• the split pin nut which is bordered in a crenellated manner on one axial side, the depressions between the battlements being able to be covered with a transverse bore of the screw and a split pin being inserted transversely.
• Disadvantages here are the necessity of making a transverse bore in the screw and, in particular, the fact that the securing against loosening only occurs in certain rotational positions of the screw element, namely when one of the depressions between the crenellations is in the transverse bore the screw covers, is possible.
• the invention has for its object to provide a screw element that is secure against unscrewing, in which no special design is required on the screw and the contact surfaces are not damaged by the securing process.
• the screw element is tightened in the usual way until the desired tension in the screw connection is reached.
• the clamping ring is then rotated on the spiral surface, as a result of which the sleeve-like attachment, which of course is of correspondingly thin-walled design, is compressed radially and is fixed on the screw with the internal thread, so that a force-locking jam against loosening on the screw is achieved. Only a relatively slight rotation of the body of the screw element and of the clamping ring relative to one another is required to bring about the jamming.
• the actual clamping connection remains unaffected by this process, because the functions of actuating the screw element to achieve the desired axial force in the screw on the one hand and securing against loosening of the screw element are completely separate from one another.
• the screw element can be tightened without the contact surfaces of securing elements being damaged and without additional moments having to be applied for the actuation or activation of securing means.
• due to the radial compression of the bush-like extension provided with the internal thread the engagement of the thread or its supporting portion increases, so that the local surface pressure can be reduced with the same axial forces of the screw connection.
• spiral surfaces to achieve radial jamming is known per se from GB-PS 293 122.
• the mutually facing U surfaces of the two rings are spiral in a cross section perpendicular to the axis of the shaft.
• the screw element with body, sleeve-like attachment and clamping ring forms the basic shape of a locking nut which, according to claim 2, is designed on the outer circumference of the body with a design for attacking a turning tool, for example on the circumference of longitudinal grooves or radial bores for attack has a hook wrench or is hexagonal in the usual way.
• the clamping ring can also have a corresponding design.
• the body of the screw element and the clamping ring can be effectively rotated against one another with high torque while simultaneously acting on two turning tools in order to produce the clamping effect on the screw.
• Fig. 2 shows a section along the line II-II in Fig. 1st
• the screw element designated 100 as a whole in FIGS. 1 and 2 represents a locking nut which can be screwed onto a screw or screw spindle 1 with an axis 2, which is only indicated by dash-dotted lines in FIG. 1.
• the screw element 100 comprises a body 3 in the form of a thick disk 4, the thickness of which in the exemplary embodiment shown is approximately a quarter of the diameter.
• the outer circumference 5 of the disk 4 is cylindrical and has four longitudinal grooves 6, which are evenly distributed over the circumference and on which a hook wrench for rotating the screw element 100 can engage.
• the body 3 On the right-hand flat side of the disk 4 in FIG. 1, the body 3 has an elevation 7 that is circular in cross-section with an outer boundary surface 8 that is perpendicular to the axis 2 and that forms the contact surface of the screw element 100 with which the screw element bears against a counter surface on a component against which the screw 1 is to be tightened.
• the washer 4 is provided with an internal thread 9 which can be screwed onto the corresponding external thread of the screw 1.
• the thread 9 continues through a sleeve-like extension 10 which is coaxial with the axis 2 and which is provided on the flat side of the disc 4 facing away from the elevation 7.
• the thread 9 thus bears on the screw 1 over the entire length of the body 3 and the shoulder 10.
• the thread pitch is dimensioned relative to the thickness of the body 3 so that there is space for several threads in the body 3 alone.
• the axial sleeve-like extension 10 has a radially continuous longitudinal slot 11 at one or more locations distributed over the circumference, which facilitates the radial compression of the extension 10.
• This radial compression is brought about by a clamping ring 20 which is rotatably arranged on the outer circumference of the axial extension and is not slotted and is provided with a large cross section in comparison to the extension because it has to absorb the ring tensile stresses which give rise to the radial forces.
• the axial extension 10 protrudes beyond the clamping ring 20 towards the side remote from the body 3 and has an outer circumferential groove 12 there for receiving a snap ring 13, by means of which the clamping ring, which is loose in the untensioned state, is held on the extension 10 and thus the body 3 remains captively connected.
• the outer circumference 15 of the clamping ring 20 is cylindrical in the exemplary embodiment and has longitudinal grooves 16 in places distributed over the circumference, in which a hook wrench can engage in order to turn the clamping ring 20 relative to the body 3.
• the clamping arrangement formed by the extension 10 and the clamping ring 20 is explained in detail with reference to FIG. 2.
• an imaginary cylindrical surface 14 with the center point on the axis 2 is indicated by dash-dotted lines.
• the outer circumferential surface 17 of the sleeve-like extension 10 is formed by a spiral surface 18 coaxial with the axis 2, the generatrices of which are parallel to the axis 2.
• the inner surface 27 of the clamping ring 20th is formed by a same spiral surface 28, which rests on the spiral surface 18 from the outside.
• the two spiral surfaces 18, 28 lie in the first two quadrants of the cross section of FIG.
• the local radius of the spiral surface 18 decreases from a point 19 of the largest radius according to FIG. 2 in a clockwise direction over almost 360 and jumps back to the largest radius at a point 21 of the smallest radius on a transition surface 22.
• the inner circumferential surface 27 of the clamping ring 20 is designed accordingly, that is, the radius decreases clockwise from a point 19 'of the largest radius to a point 21' of the smallest radius, whereupon the inner circumferential surface 27 in a transition area 22 'in a narrow angular range such as ⁇ which jumps back to position 19 'of the largest radius.
• the amount of the slope of the spiral surfaces 18, 28 in the circumferential direction is selected so that it lies in the self-locking area and, therefore, the tightening ring, once tightened, no longer turns back without external torque.
• a radius difference of 2 mm at 50 mm in diameter is obtained in the settlement a wedge with the slope ⁇ _ "2: 150, which is less equal than one degree, the Grenzwin ⁇ angle of self-locking for steel on steel at about 7.
• the spiral surfaces 18, 28 are thus far in the self-locking range, which also means that the torque applied to the clamping ring 20 is converted into radial clamping force with a high degree of efficiency.
• the tensioning arrangement 10, 20 is shown in the not yet fully tensioned state.
• the transition surfaces 22, 22 ′ are even more adjacent to one another in the circumferential direction.
• the function of the bracing can be illustrated by the Point 19 of the sleeve-like extension 10 is considered, which has the largest radius of the spiral surface 18.
• point 19 is pressed radially inward.
• the axial extension 10 is evenly compressed radially and clamped non-positively on the screw 1.
• the screw element 100 can no longer be rotated and maintains its rotational position once it has been reached.
• the radius difference of the locations 19, 21 can be approximately 2 mm for a diameter of the screw 1 of 30 to 50 mm, as in the example already mentioned.
• the screw element forming a locking nut can be tightened by rotating the body 3 until the boundary surface 8 rests on a counter surface.
• a torque which causes the tension in the screw 1 is then applied to the body 3, for example with the aid of a hook wrench which engages in the grooves 6.
• no additional moments have to be applied to secure the screw element 100, ie the entire torque applied to the circumference 5 benefits the tensioning of the screw 1.
• the tensioning ring 20 is rotated using a similar tool which engages in the grooves 16 of the tensioning ring 20.
• the sleeve-like extension 10 is radially compressed and clamped on the screw 1 in the manner described. If necessary, this tension can be held against the body 3 with another turning tool so as not to change the tension achieved for the screw 1.
• the screw element 100 is secured entirely within this element without an attack on the component forming the counter bearing for the boundary surface 8 or on the screw 1 and without the fuse depending on the material of this counter surface.
• the available length of the thread 9 is increased by the sleeve-like extension 10, and the engagement of the screw thread is also improved by the radial compression in the area of the axial extension 10.
• the body 3 does not have to be a pure mother, as in the exemplary embodiment shown, but can itself also be a component that performs another function. Also in the example, only one extension 10 with a clamping ring 20 is provided on one side, although a double-sided version and a version with two or more clamping rings on one side are also possible.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Clamps And Clips (AREA)
• Transmission Devices (AREA)
• Gripping On Spindles (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=6426488

Family Applications (1)

Country Status (6)

Families Citing this family (4)

Family Cites Families (6)

• 1991
  • 1991-03-05 DE DE19914106943 patent/DE4106943C1/de not_active Expired - Lifetime
• 1992
  • 1992-02-20 WO PCT/DE1992/000121 patent/WO1992015792A1/de not_active Application Discontinuation
  • 1992-02-20 EP EP19920905122 patent/EP0574430A1/de not_active Ceased
  • 1992-02-20 CZ CS931588A patent/CZ158893A3/cs unknown
  • 1992-02-20 JP JP4504847A patent/JPH06501092A/ja active Pending
  • 1992-02-20 CA CA 2105574 patent/CA2105574A1/en not_active Abandoned

Non-Patent Citations (1)

Also Published As

Similar Documents

Legal Events