WO2020087347A1 - 螺栓 - Google Patents
螺栓 Download PDFInfo
- Publication number
- WO2020087347A1 WO2020087347A1 PCT/CN2018/113010 CN2018113010W WO2020087347A1 WO 2020087347 A1 WO2020087347 A1 WO 2020087347A1 CN 2018113010 W CN2018113010 W CN 2018113010W WO 2020087347 A1 WO2020087347 A1 WO 2020087347A1
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- WO
- WIPO (PCT)
- Prior art keywords
- bolt
- bearing
- curved surface
- central axis
- load
- Prior art date
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- 230000003187 abdominal effect Effects 0.000 claims description 2
- 238000004088 simulation Methods 0.000 description 67
- 238000010586 diagram Methods 0.000 description 61
- 238000006073 displacement reaction Methods 0.000 description 40
- 230000000694 effects Effects 0.000 description 15
- 238000009826 distribution Methods 0.000 description 9
- 230000035939 shock Effects 0.000 description 7
- 238000000034 method Methods 0.000 description 4
- 238000005242 forging Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 206010062544 Tooth fracture Diseases 0.000 description 1
- 230000001154 acute effect Effects 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000011514 reflex Effects 0.000 description 1
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B33/00—Features common to bolt and nut
- F16B33/02—Shape of thread; Special thread-forms
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B5/00—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them
- F16B5/02—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them by means of fastening members using screw-thread
- F16B5/0241—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them by means of fastening members using screw-thread with the possibility for the connection to absorb deformation, e.g. thermal or vibrational
Definitions
- the present application relates to a bolt, in particular to a bolt that prevents loosening and breaks.
- bolts When combining multiple parts in the mechanical field, bolts are often used in combination with female threaded locks (such as nuts) to fix them.
- the body of the bolt penetrates the parts to be fixed, the head of the bolt is pressed against the part closest to the head of the bolt, and then the bolt is locked to the pair with the female thread
- the lock piece is used to clamp the plurality of parts between the head of the bolt and fix the lock piece.
- Such a fixing method may cause a loosening between the bolt and the locking member when the multiple parts encounter vibration, which in turn causes the multiple parts to loosen from each other.
- related methods have been developed to add other components to prevent the bolt and the lock from loosening. For example: add spring washers and other components between the head of the bolt and the part or between the lock and the part, apply a coating to prevent loosening between the bolt and the lock, or increase the latch bolt and the lock Pieces. In this way, additional components other than bolts and locks are required.
- the present application proposes a bolt so that when it is fitted with a female thread, it can avoid loosening when subjected to vibration without disturbing other components, and can distribute stress to avoid tooth fracture.
- An embodiment of the present application provides a bolt including a body, a head, and a threaded portion.
- the body has a central axis.
- the head is arranged at one end of the body.
- the threaded portion spirally surrounds the central axis and is connected to the body.
- the threaded portion has a bearing surface facing the head.
- the load-bearing surface is a surface with a continuous slope.
- the load-bearing surface includes a concave curved surface, a convex curved surface and a load-bearing tooth ventral surface.
- the concave curved surface touches the body.
- the convex curved surface is farther away from the body than the concave curved surface.
- One side of the convex curved surface is connected to the concave curved surface and the convex curved surface The other side is connected to the ventral surface of the load-bearing tooth.
- An embodiment of the present application provides a bolt including a body, a head, and a threaded portion.
- the body has a central axis.
- the head is arranged at one end of the body.
- the threaded portion spirally surrounds the central axis and is connected to the body.
- the threaded portion has a bearing surface facing the head.
- the load-bearing mask has a recurve point.
- the load-bearing surface includes a concave curved surface, a convex curved surface and a load-bearing tooth ventral surface.
- the concave curved surface touches the body.
- the convex curved surface is farther from the concave surface than the concave curved surface.
- the other side of the convex curved surface is connected to the ventral surface of the load-bearing tooth.
- the load-bearing surface of the threaded portion of the bolt is a surface with a continuous slope or has an inflection point, and the load-bearing surface includes a connected convex curved surface and a concave curved surface. Touch the body.
- the threaded portion can deform compliantly when subjected to force.
- the elastic restoring force of the threaded portion can increase the positive force on the element to which the bolt is locked, thereby increasing the frictional force, so as to prevent the bolt from loosening.
- the ability of the threaded portion of the bolt to disperse stress when receiving a weight load in the direction of the central axis of the bolt body can further prevent the collapse of teeth.
- FIG. 1 is a cross-sectional view of a bolt according to an embodiment of the application.
- FIG. 2 is a partially enlarged view of the bolt of FIG. 1.
- Fig. 3 is a schematic diagram comparing strain simulation of the standard bolt, the reference bolt and the bolt of Fig. 1 when the nut is displaced by 0.15 mm.
- FIG. 4 is a schematic diagram for comparing the stress simulation of the standard bolt, the reference bolt and the bolt of FIG. 1 when the nut is displaced by 0.15 mm.
- Fig. 5 is a schematic diagram of strain simulation when comparing the standard bolt, the reference bolt and the bolt of Fig. 1 when the nut displacement is 0.30 mm.
- FIG. 6 is a schematic diagram of stress simulation when comparing the standard bolt, the reference bolt and the bolt of FIG. 1 when the nut displacement is 0.30 mm.
- FIG. 7 is a partial enlarged view of a cross section of a bolt according to another embodiment of the present application.
- FIG. 8 is a partially enlarged view of a cross section of a bolt according to another embodiment of the application.
- FIG. 29 is an enlarged partial sectional view of a bolt of another embodiment of the present application.
- FIG. 30 is a schematic diagram comparing strain simulation of the standard bolt and the bolt of FIG. 29 when the nut is displaced by 0.15 mm.
- Fig. 31 is a schematic diagram comparing the stress simulation of the standard bolt and the bolt of Fig. 29 when the nut is displaced by 0.15 mm.
- Fig. 32 is a schematic diagram comparing strain simulation of the standard bolt and the bolt of Fig. 29 when the nut displacement is 0.30 mm.
- FIG. 33 is a schematic diagram comparing the stress simulation of the standard bolt and the bolt of FIG. 29 when the nut displacement is 0.30 mm.
- FIG. 1 is a cross-sectional view of a bolt according to an embodiment of the present application
- FIG. 2 is a partial enlarged view of the cross-section of the bolt of FIG. 1.
- the bolt 1 includes a connecting portion 110, a body 11, a head portion 12, and a screw portion 13.
- the body 11 has a central axis CA.
- the head 12 is provided at one end of the body 11 via the connection portion 110.
- the screw portion 13 spirally surrounds the central axis CA and is connected to the body 11.
- the connecting portion 110 connects the body 11 and the head 12, but it is not limited thereto. In other embodiments, the connecting portion 110 may also be omitted, that is, the head 12 is directly connected to the body 11.
- connection part 110 of the bolt 1 and the body 11 penetrate the parts 91 and 92, and then the body 11 is locked to the counterlocking member having a female thread through the screw part 13 8.
- the form of the counter-locking member 8 in FIG. 1 is a nut, it is not limited to this, and may be other components having female threads.
- the head 12 abuts the part 91 closest to the head 12, and the pair of locks 8 abuts the part 92 closest to the pair of locks 8.
- a plurality of parts 91 and 92 are sandwiched between the head 12 of the bolt 1 and the locking member 8 to be fixed.
- the screw portion 13 has a load-bearing surface 131, a non-bearing surface 132, a tooth peak T, and a tooth base B1.
- the bearing surface 131 faces the head 12.
- the non-weight-bearing surface 132 faces away from the head 12.
- the tooth peak T is located at the position where the screw portion 13 is farthest from the central axis CA
- the tooth bottom B1 is located at the position closest to the central axis CA in the screw portion 13.
- the side of the load-bearing surface 131 away from the central axis CA and the side of the non-bearing surface 132 away from the central axis CA are connected to the tooth peak T.
- the side of the load-bearing surface 131 close to the central axis CA and the side of the non-bearing surface 132 close to the central axis CA are connected to the tooth bottom B1 and touch the body 11.
- the load bearing surface 131 is a curved surface having a continuous slope.
- the load-bearing surface 131 includes a concave curved surface 131a, a convex curved surface 131b, and a load-bearing tooth ventral surface 131c, and has an inflexion point IP.
- the concave curved surface 131a touches the body 11 at the tooth bottom B1.
- the convex curved surface 131b is farther away from the body 11 than the concave curved surface 131a.
- One side of the convex curved surface 131b is connected to the concave curved surface 131a via the inflexion point IP.
- the other side of the convex curved surface 131b is connected to the abdominal surface 131c of the load-bearing tooth.
- the side of the load-bearing surface 131 away from the body 11 is connected to the non-bearing surface 132 at the tooth peak T.
- the inflexion point IP is located at the intersection of the concave curved surface 131a and the convex curved surface 131b.
- the concave curved surface 131a is located between the inflexion point IP and the body 11.
- the projection 131a 'of the concave curved surface 131a to the central axis CA is located between the projection IP' of the inflexion point IP to the central axis CA and the projection B1 'of the tooth base B1 to the central axis CA.
- the cross-sectional view angle of the ventral surface 131c of the load-bearing tooth in FIG. 2 may also be a convex curve or a concave curve.
- the radius of curvature of the web surface 131 c of the load-bearing tooth is greater than the radius of curvature of the convex curved surface 131 b.
- the non-bearing surface 132 includes a connecting surface 132a and a non-bearing tooth ventral surface 132b.
- One side of the connection surface 132a touches the body 11.
- the other side of the connection surface 132a is connected to the non-load-bearing tooth ventral surface 132b.
- the cross-sectional viewing angle of the non-load-bearing tooth ventral surface 132b in FIG. 2 is a straight line, but not limited to this.
- the cross-sectional viewing angle of the non-load-bearing tooth ventral surface 132b in FIG. 2 may also be a convex curve or a concave curve.
- the angle ⁇ 1 between the tangent of the inflexion point IP and the central axis CA is 75 ° to 90 °, preferably 77.5 ° to 82.5 °.
- the furthest distance from the threaded portion 13 to the body 11, that is, the vertical distance from the tooth peak T to the tooth base B1 in the radial direction of the body 11 is the tooth height H1.
- the distance H2 from the inflexion point IP to the body 11 is 3/8 to 1/2 of the tooth height H1.
- the projected length P1 of the load-bearing surface 131 to the central axis CA is substantially the same as the projected length P2 of the non-bearing surface 132 to the central axis CA.
- the technical feature that the load-bearing surface 131 is a curved surface with a continuous slope may allow manufacturing errors. For example, allow for errors due to forging technical reasons. In addition, errors due to roughness are also tolerated. In other words, the surface of the load-bearing surface 131 is allowed to exclude roughness errors or forging errors, and the curve that is roughly fitted is a case where the slope is continuous.
- FIG. 3 is a schematic diagram of strain simulation when comparing the standard bolt, reference bolt and the bolt of Fig. 1 when the nut displacement is 0.15mm
- Fig. 4 is a comparison of the standard bolt, reference bolt and the diagram
- Figure 5 is the schematic diagram of the strain simulation when the standard bolt and reference bolt are compared with the bolt of FIG. 1 when the nut is displaced by 0.30mm.
- the schematic diagram of the stress simulation of the bolt 1 when the nut displacement is 0.30mm.
- the standard bolt M10 refers to a bolt that conforms to the M10JIS standard and has a pitch of 1.5 mm between threads.
- the reference bolt RB refers to a bolt with an arc-shaped groove dug on the load-bearing surface close to the central axis on the basis of the standard bolt M10 to connect the tooth bottom.
- the load-bearing surface of the reference bolt RB has an arc-shaped groove and the same thread profile as the original standard bolt M10, referred to herein as M10 thread.
- M10 thread the original standard bolt M10
- the arc-shaped groove and the M10 thread profile are connected at a folded angle. Therefore, the slope at the corner is discontinuous and does not have an inflection point.
- H2 / H1 is substantially 1/2
- ⁇ 1 is substantially 80.5 °.
- FIG. 3 and 4 illustrate the case where the nut is displaced downward by 0.15 mm.
- the nut approximately strains the first to second threads of the standard bolt M10
- the nut approximately strains the first to fourth threads of the reference bolt RB
- the nut causes the first to fifth threads of the bolt 1 to be strained.
- the standard bolt M10 disperses the stress to the first to third threads approximately
- the reference bolt RB disperses the stress to the first to fifth threads approximately
- the bolt 1 disperses the stress to the first One to fifth thread.
- the stress distribution of the bolts of bolt 1 is more uniform.
- FIG 5 and 6 illustrate the case where the nut is displaced downward by 0.30 mm.
- the nut approximately strains the first to second threads of the standard bolt M10
- the nut approximately strains the first to fourth threads of the reference bolt RB
- the nut causes the first to fifth threads of the bolt 1 to be strained.
- the standard bolt M10 approximately distributes the stress to the first to fourth thread
- the reference bolt RB approximately distributes the stress to the first to fifth thread
- the bolt 1 approximately distributes the stress to the first One to fifth thread.
- the stress distribution of the bolts of bolt 1 is more uniform.
- bolt 1 has more threads generating strain, so more threads can generate elastic restoring force to increase the positive force on the nut, which in turn increases Friction. Therefore, the bolt 1 can achieve the effect of preventing loosening during the shock. Furthermore, the stress distribution of the bolts of the bolt 1 is relatively uniform, so the stress can be dispersed, and the effect of preventing tooth collapse can be achieved.
- FIG. 7 is an enlarged partial sectional view of a bolt according to another embodiment of the present application.
- the bolt 2 of FIG. 7 is substantially similar to the bolt 1 of FIG. 1, and the similarities between the two are not repeated here.
- the difference between the two is that: the projection length P3 of the load bearing surface 231 of the bolt 2 to the central axis CA of FIG. 7 is smaller than the projection length P4 of the non-load bearing surface 232 to the central axis CA.
- the bottom B2 of the bolt 2 is farther away from the head of the bolt 2 than the bottom B1 of the bolt 1.
- the projection 231a 'of the concave curved surface 231a to the central axis CA is located between the projection IP' of the inflexion point IP to the central axis CA and the projection B2 'of the tooth bottom B2 to the central axis CA. Furthermore, comparing the screw portion 23 of the bolt 2 with the screw portion 13 of the bolt 1, the screw portion 23 has a larger volume 230 on the non-load-bearing surface 232 side, so the screw portion 23 has a higher mechanical strength.
- the angle ⁇ 1 between the tangent of the inflexion point IP of the load bearing surface 231 of the bolt 2 and the central axis CA is 75 ° to 90 °, preferably 77.5 ° to 82.5 °.
- the vertical distance from the tooth peak T to the tooth base B2 in the radial direction of the body 21 is the tooth height H3.
- the distance H4 from the inflexion point IP to the body 21 is 3/8 to 1/2 of the tooth height H3.
- the concave curved surface 231a of the load-bearing surface 231 near the tooth bottom B2 is fitted to a circular arc with a smaller radius of curvature
- the connecting surface 232a of the non-bearing surface 232 is fitted to a circular arc with a larger radius of curvature , but not limited to this.
- FIG. 8 is a partially enlarged view of a cross section of another embodiment of the present application.
- the angle ⁇ 1 between the tangent of the inflexion point IP of the load bearing surface 331 of the bolt 3 of FIG. 8 and the central axis CA is 75 ° to 90 °, preferably 77.5 ° to 82.5 °.
- the vertical distance from the tooth peak T to the tooth base B3 in the radial direction of the body 31 is the tooth height H5.
- the distance H6 from the reflex point IP to the body 31 is 3/8 to 1/2 of the tooth height H5.
- the bolt 3 of FIG. 8 is substantially similar to the bolt 2 of FIG. 7, and the similarities between the two are not repeated here.
- the difference between the two is that in the bolt 3 of FIG. 8, the concave curved surface 331a of the bearing surface 331 is fitted to the first geometric curve OV1.
- the connecting surface 332a of the non-bearing surface 332 of the bolt 3 is fitted to the second geometric curve OV2.
- the first geometric curve OV1 has a first axis of symmetry SA1
- the second geometric curve OV2 has a second axis of symmetry SA2.
- the first geometric curve OV1 is different from the second geometric curve OV2.
- the first axis of symmetry SA1 and the second axis of symmetry SA2 overlap and penetrate the tooth base B3, and the angle ⁇ 2 between the two and the central axis CA is substantially 90 °.
- the first geometric curve OV1 is a long and narrow ellipse
- the second geometric curve OV2 is a round ellipse, but not limited to this.
- the first geometric curve OV1 and the second geometric curve OV2 may also be geometric curves such as one of the hyperbola or parabola.
- the types of geometric curves of the first geometric curve OV1 and the second geometric curve OV2 may be different.
- FIG. 9 and 10 illustrate the case where the nut is displaced downward by 0.15 mm. As shown in FIG. 9, the nut approximately strains the first to second threads of the standard bolt M10, and the nut approximately strains the first to fifth threads of the bolt 2-1 . As shown in FIG. 10, the standard bolt M10 approximately distributes the stress to the first to third threads, and the bolt 2-1 approximately distributes the stress to the first to fifth threads.
- 11 and 12 illustrate the case where the nut is displaced downward by 0.30 mm. As shown in FIG. 11, the nut approximately strains the first to second threads of the standard bolt M10, and the nut approximately strains the first to fifth threads of the bolt 2-1 . As shown in FIG. 12, the standard bolt M10 approximately distributes the stress to the first to fourth threads, and the bolt 2 approximately distributes the stress to the first to fifth threads.
- the bolt 2-1 has more threads generating strain, so there are more threads that can generate elastic restoring force to increase the positive force on the nut, thereby increasing the friction . Therefore, the bolt 2-1 can achieve the effect of preventing loosening during the shock.
- the stress distribution of the bolts of the bolt 2-1 is relatively uniform, so the stress can be dispersed and the effect of preventing tooth collapse can be achieved.
- Figure 13 is a schematic diagram of the strain simulation when the nut is displaced by 0.15mm
- Figure 14 is a schematic diagram of the stress simulation when the nut is displaced by 0.15mm
- Figure 15 is a schematic diagram of the strain simulation when the nut is displaced by 0.30mm
- Figure 16 It is a schematic diagram of stress simulation when the nut displacement is 0.30mm.
- FIG. 13 and 14 illustrate the case where the nut is displaced downward by 0.15 mm.
- the nut approximately strains the first to second threads of the standard bolt M10
- the nut approximately strains the first to fifth threads of the bolt 2-2
- the nut causes the first to fifth thread of the bolt 2-3 to be strained
- the nut causes the first to fifth thread of the bolt 2-1 to be strained
- the nut approximately The first to fourth threads of the bolt 2-4 are strained
- the nut causes the first to fifth threads of the bolt 2-5 to be strained.
- the standard bolt M10 disperses the stress to the first to third thread approximately, and the bolt 2-2, the bolt 2-3, the bolt 2-1, the bolt 2-4, and the bolt 2-5 each approximately Disperse the stress to the first to fifth thread.
- 15 and 16 illustrate the case where the nut is displaced downward by 0.30 mm.
- the nut approximately strains the first to second threads of the standard bolt M10
- the nut approximately strains the first to fifth threads of the bolt 2-2
- the nut causes the first to fifth thread of the bolt 2-3 to be strained
- the nut causes the first to fifth thread of the bolt 2-1 to be strained
- the nut approximately The first to fourth threads of the bolt 2-4 are strained
- the nut causes the first to fifth threads of the bolt 2-5 to be strained.
- the standard bolt M10 approximately distributes the stress to the first to third threads.
- the bolt 2-2, bolt 2-3, bolt 2-1, bolt 2-4, and bolt 2-5 are each approximately Disperse the stress to the first to fifth thread.
- Figure 17 is a schematic diagram of the strain simulation when the nut is displaced by 0.15mm
- Figure 18 is a schematic diagram of the stress simulation when the nut is displaced by 0.15mm
- Figure 19 is a schematic diagram of the strain simulation when the nut is displaced by 0.30mm
- Figure 20 It is a schematic diagram of stress simulation when the nut displacement is 0.30mm.
- 17 and 18 illustrate the case where the nut is displaced downward by 0.15 mm.
- the nut approximately strains the first to second threads of standard bolt M10, and the nut approximately causes bolt 2-6, bolt 2-7, bolt 2-1, and bolt 2-8 The first to fifth thread of each strained strain.
- the standard bolt M10 approximately distributes the stress to the first to third threads, and the bolts 2-6, 2-7, 2-1, and 2-8 each approximately distribute the stress to the first One to fifth thread.
- 19 and 20 illustrate the case where the nut is displaced downward by 0.30 mm.
- the nut approximately strains the first to second threads of standard bolt M10, and the nut approximately causes bolt 2-6, bolt 2-7, bolt 2-1, and bolt 2-8 The first to fifth thread of each strained strain.
- the standard bolt M10 approximately distributes the stress to the first to third threads, and the bolts 2-6, 2-7, 2-1, and 2-8 each approximately distribute the stress to the first One to fifth thread.
- the parameter H4 / H3 5/8 of the bolts 2-8 exceeds the above parameter range. It can be seen from FIGS. 17 and 19 that although the nut strains the first to fifth threads of the bolt 2-8 approximately, the body portion of the bolt 2-8 hardly sees strain. As can be seen from FIGS. 18 and 20, although the bolts 2-8 distribute the stress to the first to fifth threads, the stress is less transmitted to the body portion of the bolts 2-8. In this way, the strain and stress caused by the displacement of the nut of the bolt 2-8 are obviously concentrated on the thread of the bolt 2-8.
- FIG. 21 Schematic diagram of strain simulation when the nut is displaced by 0.15mm.
- Figure 22 is a schematic diagram of stress simulation when the nut is displaced by 0.15mm.
- Figure 23 is a schematic diagram of strain simulation when the nut is displaced by 0.30mm.
- Figure 24 is a stress simulation when the nut is displaced by 0.30mm. Simulation diagram.
- 21 and 22 illustrate the case where the nut is displaced downward by 0.15 mm.
- the nut approximately strains the first to second threads of the standard bolt M10.
- the nut approximately causes the first to third bolts of bolts 2-9 and 2-10
- the teeth are strained.
- the standard bolt M10 approximately distributes the stress to the first to third threads, and the bolts 2-9 and 2-10 each approximately distribute the stress to the first to fifth threads.
- 23 and 24 illustrate the case where the nut is displaced downward by 0.30 mm.
- the nut approximately strains the first to second threads of the standard bolt M10, and the nut approximately causes the first to third bolts of bolts 2-9 and bolts 2-10 respectively The teeth are strained.
- the standard bolt M10 approximately distributes the stress to the first to third threads, and the bolts 2-9 and 2-10 each approximately distribute the stress to the first to fifth threads.
- FIG. 25 Schematic diagram of strain simulation when the nut is displaced by 0.15mm.
- Figure 26 is a schematic diagram of stress simulation when the nut is displaced by 0.15mm.
- Figure 27 is a schematic diagram of strain simulation when the nut is displaced by 0.30mm.
- Figure 28 is a stress simulation when the nut is displaced by 0.30mm. Simulation diagram.
- 25 and 26 illustrate the case where the nut is displaced downward by 0.15 mm.
- the nut approximately strains the first to second threads of the standard bolt M10, and the nut approximately causes the first to third bolts of bolts 2-11 and 2-12 The teeth are strained.
- the standard bolt M10 approximately distributes the stress to the first to third threads, and the bolts 2-11 and 2-12 each approximately distribute the stress to the first to fifth threads.
- 27 and 28 illustrate the case where the nut is displaced downward by 0.30 mm.
- the nut approximately strains the first to second threads of the standard bolt M10, and the nut approximately causes the first to third bolts of bolts 2-11 and 2-12 The teeth are strained.
- the standard bolt M10 approximately distributes the stress to the first to third threads, and the bolts 2-11 and 2-12 each approximately distribute the stress to the first to fifth threads.
- FIG. 29 is an enlarged partial sectional view of a bolt according to another embodiment of the present application.
- the angle ⁇ 1 between the tangent of the inflexion point IP of the load bearing surface 431 of the bolt 4 of FIG. 29 and the central axis CA is 75 ° to 90 °, preferably 77.5 ° to 82.5 °.
- the difference in the vertical distance from the tooth peak T to the tooth base B4 in the radial direction of the body 41 is the tooth height H7.
- the distance H8 from the inflexion point IP to the body 41 is 3/8 to 1/2 of the tooth height H7.
- the connecting surface 432a of the non-bearing surface 432 of the bolt 4 of FIG. 29 and the concave curved surface 431a of the bearing surface 431 fit to the same geometric curve OV3.
- the geometric curve OV3 has a symmetry axis SA3.
- the axis of symmetry SA3 is offset from the tooth bottom B4, and the angle ⁇ 3 between the axis of symmetry SA3 and the central axis CA is an acute angle.
- the geometric curve OV3 is an ellipse, but not limited to this.
- the geometric curve OV3 can also be one of the hyperbolic curves or a geometric curve such as a parabola.
- the connecting surface 432a of the non-load-bearing surface 432 of the bolt 4 and the concave curved surface 431a of the load-bearing surface 431 may be fitted to the same arc line.
- Fig. 30 is a schematic diagram of strain simulation when comparing the standard bolt and the bolt of Fig. 29 when the nut displacement is 0.15mm
- Fig. 31 is a comparison of the displacement of the standard bolt and the bolt of Fig. 29 at the nut Schematic diagram of stress simulation at 0.15 mm
- Fig. 32 is a schematic diagram of strain simulation when comparing the standard bolt and the bolt of Fig. 29 when the nut displacement is 0.30 mm
- Fig. 33 is a stress simulation comparison of the standard bolt and the bolt of Fig. 29 when the nut displacement is 0.30 mm. schematic diagram.
- FIGS. 30 to 33 from left to right are the standard bolt M10 and the bolt 4 of FIG. 29.
- the nut is a nut in accordance with the M10JIS standard and the pitch between the threads is 1.5 mm, and one nut spans approximately five threads.
- the bolt 4 used has H8 / H7 of substantially 0.392 and ⁇ 1 of substantially 80.5 °.
- 30 and 31 illustrate the case where the nut is displaced downward by 0.15 mm.
- the nut approximately strains the first to second threads of the standard bolt M10
- the nut approximately strains the first to fifth threads of the bolt 4.
- the standard bolt M10 approximately distributes the stress to the first to third threads
- the bolt 4 approximately distributes the stress to the first to fifth threads.
- 32 and 33 illustrate the case where the nut is displaced downward by 0.30 mm. As shown in FIG. 32, the nut approximately strains the first to second threads of the standard bolt M10, and the nut approximately strains the first to fifth threads of the bolt 4. As shown in FIG. 33, the standard bolt M10 approximately distributes the stress to the first to fourth threads, and the bolt 4 approximately distributes the stress to the first to fifth threads.
- the bolt 4 has more threads that are strained, so there are more threads that can generate an elastic restoring force to increase the positive force on the nut, thereby increasing the friction. Therefore, the bolt 4 can achieve the effect of preventing loosening during the shock. Furthermore, since the stress distribution of the bolts of the bolt 4 is relatively uniform, the stress can be dispersed, and the effect of preventing tooth collapse can be achieved.
- the load-bearing surface of the threaded portion of the bolt is a surface with a continuous slope or has an inflection point
- the load-bearing surface includes a connected convex curved surface and a concave curved surface.
- the convex curved surface is farther from the body than the concave curved surface ,
- the concave surface touches the body.
- the threaded portion can deform compliantly when subjected to force.
- the elastic restoring force of the threaded portion can increase the positive force on the element to which the bolt is locked, thereby increasing the frictional force, so as to prevent the bolt from loosening.
- the ability of the threaded portion of the bolt to disperse stress when receiving a weight load in the direction of the central axis of the bolt body can further prevent the collapse of teeth.
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Abstract
一种螺栓(1),包含一本体(11)、一头部(12)及一螺纹部(13)。本体(11)具有一中心轴(CA),头部(12)设置于本体(11)的一端;螺纹部(13)沿中心轴(CA)螺旋围绕且连接于本体(11),螺纹部(13)具有一朝向头部(12)的承重面(131),承重面(131)为斜率连续的面或具有一反曲点(IP)。承重面(131)包含一凹曲面(131a)、一凸曲面(131b)及一承重牙腹面(131c),凹曲面(131a)触及本体(11),凸曲面(131b)较凹曲面(131a)远离本体(11),凸曲面(131b)的一侧与凹曲面(131a)相连且凸曲面(131b)的另一侧与承重牙腹面(131c)相连。
Description
本申请涉及一种螺栓,特别是涉及一种防松且防崩牙的螺栓。
于机械领域组合多个零件时,常使用螺栓搭配具有母螺纹的对锁件(如螺母)予以固定。藉由螺栓的本体贯穿欲予以固定的多个零件,将螺栓的头部抵靠于所述多个零件中最接近螺栓的头部的零件,再将螺栓锁固于所述具有母螺纹的对锁件,以将所述多个零件夹置于螺栓的头部与对锁件之间加以固定。
此种固定方式在所述多个零件遭遇震动时,可能导致螺栓与对锁件之间发生松动的情形,进而导致所述多个零件彼此松脱。为了避免螺栓与对锁件之间发生松动的情形,相关领域有发展出添增其他元件以防止螺栓与对锁件松动的手段。例如:于螺栓的头部与零件之间或对锁件与零件之间增加弹簧垫圈等元件,于螺栓与对锁件之间涂布防止松脱的涂层,或增加插销卡合螺栓与对锁件。此种方式皆需要另外增加螺栓与对锁件以外的元件。
此外,也有技术手段是在螺栓的头部或对锁件形成锯齿结构,将所述锯齿结构抵靠于所述零件,以增加摩擦力。此种方式虽然不需要另外增加螺栓与对锁件以外的元件,但在螺栓与对锁件有些微的松脱而导致锯齿结构无法紧密抵靠于所述零件时,便会失效。
另一方面,当所述多个零件受外力影响,导致螺栓与对锁件的负荷力量过大时,可能导致螺栓的螺牙的局部应力增加,而有螺牙崩毁的可能,即所谓崩牙。
发明内容
鉴于以上的问题,本申请提出一种螺栓,使其在配合母螺纹时,无须其他元件也能在遭遇震动时避免松脱,且能够分散应力以避免崩牙。
本申请的一实施例提出一种螺栓,包含一本体、一头部及一螺纹部。本体具有一中心轴。头部设置于本体的一端。螺纹部沿中心轴螺旋围绕且连接于本体。螺纹部具有一承重面朝向头部。承重面为一斜率连续的面,承重面包含一 凹曲面、一凸曲面及一承重牙腹面,凹曲面触及本体,凸曲面较凹曲面远离本体,凸曲面的一侧与凹曲面相连且凸曲面的另一侧与承重牙腹面相连。
本申请的一实施例提出一种螺栓,包含一本体、一头部及一螺纹部。本体具有一中心轴。头部设置于本体的一端。螺纹部沿中心轴螺旋围绕且连接于本体。螺纹部具有一承重面朝向头部。承重面具有一反曲点,承重面包含一凹曲面、一凸曲面及一承重牙腹面,凹曲面触及本体,凸曲面较凹曲面远离本体,凸曲面的一侧经由反曲点与凹曲面相连且凸曲面的另一侧与该承重牙腹面相连。
根据本申请的一实施例的螺栓,螺栓的螺纹部的承重面为斜率连续的面或具有反曲点,且承重面包含相连的凸曲面及凹曲面,凸曲面较凹曲面远离本体,凹曲面触及本体。借此,螺纹部能够于承受力量时顺应地产生形变。如此的螺栓在遭遇震动的过程中,螺纹部的弹性恢复力可对于此螺栓所锁附的元件增加正向力,进而增加摩擦力,以达到防止螺栓松脱的效果。此外,还能够加强螺栓的螺纹部于承受沿螺栓本体中心轴方向的重量负荷时将应力分散的能力,进而达到防止崩牙的效果。
以上的关于本申请内容的说明及以下的实施方式的说明用以示范与解释本申请的精神与原理,并且提供本申请的权利要求更进一步的解释。
此处所说明的附图用来提供对本申请的进一步理解,构成本申请的一部分,本申请的示意性实施例及其说明用于解释本申请,并不构成对本申请的不当限定。在附图中:
图1为本申请一实施例的螺栓的剖面图。
图2为图1的螺栓的剖面局部放大图。
图3为比较标准螺栓、参考螺栓与图1的螺栓于螺母位移0.15mm时的应变模拟示意图。
图4为比较标准螺栓、参考螺栓与图1的螺栓于螺母位移0.15mm时的应力模拟示意图。
图5为比较标准螺栓、参考螺栓与图1的螺栓于螺母位移0.30mm时的应变模拟示意图。
图6为比较标准螺栓、参考螺栓与图1的螺栓于螺母位移0.30mm时的应力模拟示意图。
图7为本申请另一实施例的螺栓的剖面局部放大图。
图8为本申请另一实施例的螺栓的剖面局部放大图。
图9为比较标准螺栓与图7的螺栓于θ1=80.5°且H4/H3=1/2的参数下于螺母位移0.15mm时的应变模拟示意图。
图10为比较标准螺栓与图7的螺栓于θ1=80.5°且H4/H3=1/2的参数下于螺母位移0.15mm时的应力模拟示意图。
图11为比较标准螺栓与图7的螺栓于θ1=80.5°且H4/H3=1/2的参数下于螺母位移0.30mm时的应变模拟示意图。
图12为比较标准螺栓与图7的螺栓于θ1=80.5°且H4/H3=1/2的参数下于螺母位移0.30mm时的应力模拟示意图。
图13为比较标准螺栓与图7的螺栓于θ1=75°、77.5°、80.5°、82.5°、90°且H4/H3=1/2的参数下于螺母位移0.15mm时的应变模拟示意图。
图14为比较标准螺栓与图7的螺栓于θ1=75°、77.5°、80.5°、82.5°、90°且H4/H3=1/2的参数下于螺母位移0.15mm时的应力模拟示意图。
图15为比较标准螺栓与图7的螺栓于θ1=75°、77.5°、80.5°、82.5°、90°且H4/H3=1/2的参数下于螺母位移0.30mm时的应变模拟示意图。
图16为比较标准螺栓与图7的螺栓于θ1=75°、77.5°、80.5°、82.5°、90°且H4/H3=1/2的参数下于螺母位移0.30mm时的应力模拟示意图。
图17为比较标准螺栓与图7的螺栓于θ1=80.5°且H4/H3=3/8、7/16、1/2、5/8的参数下于螺母位移0.15mm时的应变模拟示意图。
图18为比较标准螺栓与图7的螺栓于θ1=80.5°且H4/H3=3/8、7/16、1/2、5/8的参数下于螺母位移0.15mm时的应力模拟示意图。
图19为比较标准螺栓与图7的螺栓于θ1=80.5°且H4/H3=3/8、7/16、1/2、5/8的参数下于螺母位移0.30mm时的应变模拟示意图。
图20为比较标准螺栓与图7的螺栓于θ1=80.5°且H4/H3=3/8、7/16、1/2、5/8的参数下于螺母位移0.30mm时的应力模拟示意图。
图21为比较标准螺栓与图7的螺栓于θ1=77.5°、82.5°且H4/H3=7/16的参数下于螺母位移0.15mm时的应变模拟示意图。
图22为比较标准螺栓与图7的螺栓于θ1=77.5°、82.5°且H4/H3=7/16的参数下于螺母位移0.15mm时的应力模拟示意图。
图23为比较标准螺栓与图7的螺栓于θ1=77.5°、82.5°且H4/H3=7/16的参数下于螺母位移0.30mm时的应变模拟示意图。
图24为比较标准螺栓与图7的螺栓于θ1=77.5°、82.5°且H4/H3=7/16的参数下于螺母位移0.30mm时的应力模拟示意图。
图25为比较标准螺栓与图7的螺栓于θ1=77.5°、82.5°且H4/H3=3/8的参数下于螺母位移0.15mm时的应变模拟示意图。
图26为比较标准螺栓与图7的螺栓于θ1=77.5°、82.5°且H4/H3=3/8的参数下于螺母位移0.15mm时的应力模拟示意图。
图27为比较标准螺栓与图7的螺栓于θ1=77.5°、82.5°且H4/H3=3/8的参数下于螺母位移0.30mm时的应变模拟示意图。
图28为比较标准螺栓与图7的螺栓于θ1=77.5°、82.5°且H4/H3=3/8的参数下于螺母位移0.30mm时的应力模拟示意图。
图29为本申请另一实施例的螺栓的剖面局部放大图。
图30为比较标准螺栓与图29的螺栓于螺母位移0.15mm时的应变模拟示意图。
图31为比较标准螺栓与图29的螺栓于螺母位移0.15mm时的应力模拟示意图。
图32为比较标准螺栓与图29的螺栓于螺母位移0.30mm时的应变模拟示意图。
图33为比较标准螺栓与图29的螺栓于螺母位移0.30mm时的应力模拟示意图。
以下在实施方式中详细叙述本申请之实施例的详细特征以及优点,其内容足以使任何本领域技术人员了解本申请实施例的技术内容并据以实施,且根据本说明书所公开的内容、权利要求及图式,任何本领域技术人员可轻易地理解本申请相关的目的及优点。以下实施例进一步详细说明本申请的观点,但非以任何观点限制本申请的范畴。
本说明书所谓的示意图中,由于用以说明而可有尺寸、比例及角度等较为夸张的情形,但并非用以限定本申请。于未违背本申请要旨的情况下能够有各种变更。实施例及图式的描述中所提及的上下前后方位为用以说明,而并非用以限定本申请。
请参照图1及图2,图1为本申请一实施例的螺栓的剖面图,图2为图1的螺栓的剖面局部放大图。
于本实施例中,螺栓1包含连接部110、本体11、头部12及螺纹部13。本体11具有中心轴CA。头部12经由连接部110而设置于本体11的一端。螺纹部13沿中心轴CA螺旋围绕且连接于本体11。连接部110连接本体11与头部12,但不以此为限。于其他实施例中,也可省略连接部110,即头部12直接连接于本体11。
如图1所示,于组合多个零件91、92时,螺栓1的连接部110及本体11贯穿零件91、92,再将本体11经由螺纹部13而锁固于具有母螺纹的对锁件8。图1中的对锁件8的形式虽为螺母,但不以此为限,也可为其他具有母螺纹的元件。头部12抵靠于最接近头部12的零件91,对锁件8抵靠于最接近对锁件8的零件92。多个零件91、92被夹置于螺栓1的头部12与对锁件8之间加以固定。
如图2所示,螺纹部13具有承重面131、非承重面132、牙峰T及牙底B1。承重面131朝向头部12。非承重面132背向头部12。牙峰T位于螺纹部13最远离中心轴CA的位置,牙底B1位于螺纹部13最接近中心轴CA的位置。承重面131远离中心轴CA的一侧与非承重面132远离中心轴CA的一侧相连于牙峰T。承重面131接近中心轴CA的一侧与非承重面132接近中心轴CA的一侧相连于牙底B1且触及本体11。
承重面131为斜率连续的曲面。承重面131包含凹曲面131a、凸曲面131b及承重牙腹面131c,且具有反曲点IP。凹曲面131a于牙底B1处触及本体11。凸曲面131b较凹曲面131a远离本体11。凸曲面131b的一侧经由反曲点IP与凹曲面131a相连。凸曲面131b的另一侧与承重牙腹面131c相连。承重面131远离本体11的一侧于牙峰T处与非承重面132相连。反曲点IP位于凹曲面131a及凸曲面131b的交接处。凹曲面131a位于反曲点IP与本体11之间。凹曲面131a至中心轴CA的投影131a’位于反曲点IP至中心轴CA的投影IP’ 与牙底B1至中心轴CA的投影B1’之间。于本实施例中,承重牙腹面131c于图2的剖面视角为直线,但不以此为限。于其他实施例中,承重牙腹面131c于图2的剖面视角也可为凸曲线或凹曲线。但于图2的剖面视角中,在承重牙腹面131c为凸曲线的情况下,承重牙腹面131c的曲率半径大于凸曲面131b的曲率半径。
于本实施例中,非承重面132包括连接面132a及非承重牙腹面132b。连接面132a的一侧触及本体11。连接面132a的另一侧与非承重牙腹面132b相连。于本实施例中,非承重牙腹面132b于图2的剖面视角为直线,但不以此为限。于其他实施例中,非承重牙腹面132b于图2的剖面视角也可为凸曲线或凹曲线。
于本实施例中,反曲点IP的切线与中心轴CA的夹角θ1为75°~90°,较佳为77.5°~82.5°。螺纹部13至本体11的最远距离,即牙峰T至牙底B1沿本体11的径向的垂直距离为牙高H1。反曲点IP至本体11的距离H2为牙高H1的3/8~1/2。承重面131至中心轴CA的投影长度P1与非承重面132至中心轴CA的投影长度P2实质上相同。
于本实施例中,承重面131为斜率连续的曲面的技述特征得容许制造上的误差。举例而言,容许因锻造技术上的原因而造成的误差。此外,也容许因粗糙度的原因而造成的误差。换言之,容许承重面131的表面排除粗糙度误差或锻造误差而大致拟合的曲线为斜率连续的情形。
请参照图3、图4、图5及图6,图3为比较标准螺栓、参考螺栓与图1的螺栓于螺母位移0.15mm时的应变模拟示意图,图4为比较标准螺栓、参考螺栓与图1的螺栓于螺母位移0.15mm时的应力模拟示意图,图5为比较标准螺栓、参考螺栓与图1的螺栓于螺母位移0.30mm时的应变模拟示意图,图6为比较标准螺栓、参考螺栓与图1的螺栓于螺母位移0.30mm时的应力模拟示意图。
图3~图6中,由左至右分别为标准螺栓M10、参考螺栓RB与图1的螺栓1。于此模拟中,螺母为依照M10JIS标准且螺牙间的牙距为1.5mm的螺母,一个螺母约跨越五个螺牙。标准螺栓M10指的是依照M10JIS标准且螺牙间的牙距为1.5mm的螺栓。参考螺栓RB指的是在标准螺栓M10的基础上,于承重面接近中心轴侧挖出弧形凹槽连接牙底的螺栓。因此,参考螺栓RB的承重 面具有弧形凹槽及与原标准螺栓M10相同的螺纹轮廓,在此简称为M10螺纹。其中,所述弧形凹槽与所述M10螺纹轮廓以折角连接。因此,于所述折角处的斜率不连续,且不具有反曲点。所使用的螺栓1,其H2/H1实质上为1/2,θ1实质上为80.5°。
图3与图4说明螺母往下位移0.15mm的情况。如图3所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使参考螺栓RB的第一个至第四个螺牙产生有应变的情况,螺母约使螺栓1的第一个至第五个螺牙产生有应变的情况。如图4所示,标准螺栓M10约将应力分散至第一个至第三个螺牙,参考螺栓RB约将应力分散至第一个至第五个螺牙,螺栓1约将应力分散至第一个至第五个螺牙。但相较于参考螺栓RB,螺栓1的众螺牙所分担的应力分布较为均匀。
图5与图6说明螺母往下位移0.30mm的情况。如图5所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使参考螺栓RB的第一个至第四个螺牙产生有应变的情况,螺母约使螺栓1的第一个至第五个螺牙产生有应变的情况。如图6所示,标准螺栓M10约将应力分散至第一个至第四个螺牙,参考螺栓RB约将应力分散至第一个至第五个螺牙,螺栓1约将应力分散至第一个至第五个螺牙。但相较于参考螺栓RB,螺栓1的众螺牙所分担的应力分布较为均匀。
由上可知,相较于标准螺栓M10与参考螺栓RB,螺栓1具有更多螺牙产生有应变的情况,所以有较多个螺牙能产生弹性恢复力以对螺母增加正向力,进而增加摩擦力。因此,螺栓1可在遭遇震动的过程中达到防止松脱的效果。再者,螺栓1的众螺牙所分担的应力分布较为均匀,所以能分散应力,进而达到防止崩牙的效果。
而且,比较螺母的位移为0.15mm及0.30mm的情况,螺栓1的螺纹部所产生的应变与所受到的应力皆没有显著变化。因此,在螺母因震动而具有相异的位移时,螺栓1的螺纹部的应变与应力皆未有显著变化,所以螺栓1与螺母的摩擦力也不会有显著变化,而可认为螺栓1不会受到震动的影响而产生松脱的问题。
请参照图7,为本申请另一实施例的螺栓的剖面局部放大图。图7的螺栓2与图1的螺栓1大致上相似,在此不加赘述二者相同之处。二者的差异在于: 图7的螺栓2的承重面231至中心轴CA的投影长度P3小于非承重面232至中心轴CA的投影长度P4。换言之,螺栓2的牙底B2较螺栓1的牙底B1向下远离螺栓2的头部。凹曲面231a至中心轴CA的投影231a’位于反曲点IP至中心轴CA的投影IP’与牙底B2至中心轴CA的投影B2’之间。而且,比较螺栓2的螺纹部23与螺栓1的螺纹部13,螺纹部23的非承重面232侧具有较多的体积230,所以螺纹部23具有较高的机械强度。
螺栓2的承重面231的反曲点IP的切线与中心轴CA的夹角θ1为75°~90°,较佳为77.5°~82.5°。牙峰T至牙底B2沿本体21的径向的垂直距离为牙高H3。反曲点IP至本体21的距离H4为牙高H3的3/8~1/2。
于本实施例中,于牙底B2附近的承重面231的凹曲面231a拟合于较小曲率半径的圆弧线,非承重面232的连接面232a拟合于较大曲率半径的圆弧线,但不以此为限。
举例而言,请参照图8,为本申请另一实施例的螺栓的剖面局部放大图。图8的螺栓3的承重面331的反曲点IP的切线与中心轴CA的夹角θ1为75°~90°,较佳为77.5°~82.5°。牙峰T至牙底B3沿本体31的径向的垂直距离为牙高H5。反曲点IP至本体31的距离H6为牙高H5的3/8~1/2。
图8的螺栓3与图7的螺栓2大致上相似,在此不加赘述二者相同之处。二者的差异在于:图8的螺栓3中,承重面331的凹曲面331a拟合于第一几何曲线OV1。螺栓3的非承重面332的连接面332a拟合于第二几何曲线OV2。第一几何曲线OV1具有第一对称轴SA1,第二几何曲线OV2具有第二对称轴SA2。第一几何曲线OV1相异于第二几何曲线OV2。第一对称轴SA1及第二对称轴SA2重合并贯穿牙底B3,且二者与中心轴CA的夹角θ2为实质上90°。
于本实施例中,第一几何曲线OV1为狭长的椭圆线,第二几何曲线OV2为浑圆的椭圆线,但不以此为限。第一几何曲线OV1及第二几何曲线OV2也可为双曲线的其中一曲线或拋物线等几何曲线。而且,第一几何曲线OV1及第二几何曲线OV2的几何曲线种类也可相异。
请参照图9、图10、图11及图12,图9为比较标准螺栓与图7的螺栓于θ1=80.5°且H4/H3=1/2的参数下于螺母位移0.15mm时的应变模拟示意图,图10为比较标准螺栓M10与图7的螺栓于θ1=80.5°且H4/H3=1/2的参数下于螺母位移0.15mm时的应力模拟示意图,图11为比较标准螺栓M10与图7 的螺栓于θ1=80.5°且H4/H3=1/2的参数下于螺母位移0.30mm时的应变模拟示意图,图12为比较标准螺栓M10与图7的螺栓于θ1=80.5°且H4/H3=1/2的参数下于螺母位移0.30mm时的应力模拟示意图。
图9~图12中,由左至右分别为标准螺栓M10与螺栓2-1。于此模拟中,螺母为依照M10JIS标准且螺牙间的牙距为1.5mm的螺母,一个螺母约跨越五个螺牙。所使用的螺栓2-1,为于图7的螺栓2的基础上,参数为θ1=80.5°且H4/H3=1/2的螺栓。
图9与图10说明螺母往下位移0.15mm的情况。如图9所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使螺栓2-1的第一个至第五个螺牙产生有应变的情况。如图10所示,标准螺栓M10约将应力分散至第一个至第三个螺牙,螺栓2-1约将应力分散至第一个至第五个螺牙。
图11与图12说明螺母往下位移0.30mm的情况。如图11所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使螺栓2-1的第一个至第五个螺牙产生有应变的情况。如图12所示,标准螺栓M10约将应力分散至第一个至第四个螺牙,螺栓2约将应力分散至第一个至第五个螺牙。
由上可知,相较于标准螺栓M10,螺栓2-1具有更多螺牙产生有应变的情况,所以有较多个螺牙能产生弹性恢复力以对螺母增加正向力,进而增加摩擦力。因此,螺栓2-1可在遭遇震动的过程中达到防止松脱的效果。再者,螺栓2-1的众螺牙所分担的应力分布较为均匀,所以能分散应力,进而达到防止崩牙的效果。
而且,比较螺母的位移为0.15mm及0.30mm的情况,螺栓2-1的螺纹部所产生的应变与所受到的应力皆没有显著变化。因此,在螺母因震动而具有相异的位移时,螺栓2-1的螺纹部的应变与应力皆未有显著变化,所以螺栓2-1与螺母的摩擦力也不会有显著变化,而可认为螺栓2-1不会受到震动的影响而产生松脱的问题。
以下,就θ1=75°~90°且H4/H3=3/8~1/2的参数进行比较。
请参照图13、图14、图15及图16,为比较标准螺栓与图7的螺栓于θ1=75°、77.5°、80.5°、82.5°、90°且H4/H3=1/2的参数下的模拟示意图,其中 图13为于螺母位移0.15mm时的应变模拟示意图,图14为于螺母位移0.15mm时的应力模拟示意图,图15为于螺母位移0.30mm时的应变模拟示意图,图16为于螺母位移0.30mm时的应力模拟示意图。
图13~图16中,由左至右分别为标准螺栓M10、“θ1=75°且H4/H3=1/2的螺栓2-2”、“θ1=77.5°且H4/H3=1/2的螺栓2-3”、“θ1=80.5°且H4/H3=1/2的螺栓2-1”、“θ1=82.5°且H4/H3=1/2的螺栓2-4”与“θ1=90°且H4/H3=1/2的螺栓2-5”。于此模拟中,螺母为依照M10JIS标准且螺牙间的牙距为1.5mm的螺母,一个螺母约跨越五个螺牙。
图13与图14说明螺母往下位移0.15mm的情况。如图13所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使螺栓2-2的第一个至第五个螺牙产生有应变的情况,螺母约使螺栓2-3的第一个至第五个螺牙产生有应变的情况,螺母约使螺栓2-1的第一个至第五个螺牙产生有应变的情况,螺母约使螺栓2-4的第一个至第四个螺牙产生有应变的情况,螺母约使螺栓2-5的第一个至第五个螺牙产生有应变的情况。
如图14所示,标准螺栓M10约将应力分散至第一个至第三个螺牙,螺栓2-2、螺栓2-3、螺栓2-1、螺栓2-4及螺栓2-5各自约将应力分散至第一个至第五个螺牙。
图15与图16说明螺母往下位移0.30mm的情况。如图15所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使螺栓2-2的第一个至第五个螺牙产生有应变的情况,螺母约使螺栓2-3的第一个至第五个螺牙产生有应变的情况,螺母约使螺栓2-1的第一个至第五个螺牙产生有应变的情况,螺母约使螺栓2-4的第一个至第四个螺牙产生有应变的情况,螺母约使螺栓2-5的第一个至第五个螺牙产生有应变的情况。
如图16所示,标准螺栓M10约将应力分散至第一个至第三个螺牙,螺栓2-2、螺栓2-3、螺栓2-1、螺栓2-4及螺栓2-5各自约将应力分散至第一个至第五个螺牙。
由上可知,相较于标准螺栓M10,各种满足θ1=75°~90°且H4/H3=1/2的参数的螺栓2-2、螺栓2-3、螺栓2-1、螺栓2-4及螺栓2-5各自具有更多螺牙产生有应变的情况,所以有较多个螺牙能产生弹性恢复力以对螺母增加正向力,进而增加摩擦力。因此,满足上述参数的螺栓2-2、螺栓2-3、螺栓2-1、 螺栓2-4及螺栓2-5各自可在遭遇震动的过程中达到防止松脱的效果。再者,螺栓2-2、螺栓2-3、螺栓2-1、螺栓2-4及螺栓2-5各自的众螺牙所分担的应力分布较为均匀,所以能分散应力,进而达到防止崩牙的效果。
而且,比较螺母的位移为0.15mm及0.30mm的情况,满足上述参数的螺栓2-2、螺栓2-3、螺栓2-1、螺栓2-4及螺栓2-5各自的螺纹部所产生的应变与所受到的应力皆没有显著变化。因此,在螺母因震动而具有相异的位移时,螺栓2-2、螺栓2-3、螺栓2-1、螺栓2-4及螺栓2-5各自的螺纹部的应变与应力皆未有显著变化,所以螺栓2-2、螺栓2-3、螺栓2-1、螺栓2-4及螺栓2-5各自与螺母的摩擦力也不会有显著变化,而可认为螺栓2-2、螺栓2-3、螺栓2-1、螺栓2-4及螺栓2-5不会受到震动的影响而产生松脱的问题。
请参照图17、图18、图19及图20,为比较标准螺栓与图7的螺栓于θ1=80.5°且H4/H3=3/8、7/16、1/2、5/8的参数下的模拟示意图,其中图17为于螺母位移0.15mm时的应变模拟示意图,图18为于螺母位移0.15mm时的应力模拟示意图,图19为于螺母位移0.30mm时的应变模拟示意图,图20为于螺母位移0.30mm时的应力模拟示意图。
图17~图20中,由左至右分别为标准螺栓M10、“θ1=80.5°且H4/H3=3/8的螺栓2-6”、“θ1=80.5°且H4/H3=7/16的螺栓2-7”、“θ1=80.5°且H4/H3=1/2的螺栓2-1”与“θ1=80.5°且H4/H3=5/8的螺栓2-8”。于此模拟中,螺母为依照M10JIS标准且螺牙间的牙距为1.5mm的螺母,一个螺母约跨越五个螺牙。
图17与图18说明螺母往下位移0.15mm的情况。如图17所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使螺栓2-6、螺栓2-7、螺栓2-1及螺栓2-8各自的第一个至第五个螺牙产生有应变的情况。如图18所示,标准螺栓M10约将应力分散至第一个至第三个螺牙,螺栓2-6、螺栓2-7、螺栓2-1及螺栓2-8各自约将应力分散至第一个至第五个螺牙。
图19与图20说明螺母往下位移0.30mm的情况。如图19所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使螺栓2-6、螺栓2-7、螺栓2-1及螺栓2-8各自的第一个至第五个螺牙产生有应变的情况。如图20所示,标准螺栓M10约将应力分散至第一个至第三个螺牙,螺栓2-6、螺栓2-7、螺栓2-1及螺栓2-8各自约将应力分散至第一个至第五个螺牙。
由上可知,相较于标准螺栓M10,各种满足θ1=80.5°且H4/H3=3/8~1/2的参数的螺栓2-6、螺栓2-7及螺栓2-1各自具有更多螺牙产生有应变的情况,所以有较多个螺牙能产生弹性恢复力以对螺母增加正向力,进而增加摩擦力。因此,满足上述参数的螺栓2-6、螺栓2-7及螺栓2-1各自可在遭遇震动的过程中达到防止松脱的效果。再者,螺栓2-6、螺栓2-7及螺栓2-1各自的众螺牙所分担的应力分布较为均匀,所以能分散应力,进而达到防止崩牙的效果。
而且,比较螺母的位移为0.15mm及0.30mm的情况,满足上述参数的螺栓2-6、螺栓2-7及螺栓2-1各自的螺纹部所产生的应变与所受到的应力皆没有显著变化。因此,在螺母因震动而具有相异的位移时,螺栓2-6、螺栓2-7及螺栓2-1各自的螺纹部的应变与应力皆未有显著变化,所以螺栓2-6、螺栓2-7及螺栓2-1各自与螺母的摩擦力也不会有显著变化,而可认为螺栓2-6、螺栓2-7及螺栓2-1不会受到震动的影响而产生松脱的问题。
然而,螺栓2-8的参数H4/H3=5/8超出上述参数范围。由图17及图19可知,虽然螺母约使螺栓2-8的第一个至第五个螺牙产生有应变的情况,但螺栓2-8的本体部分却几乎未见有应变。由图18及图20可知,虽然螺栓2-8将应力分散至第一个至第五个螺牙,但应力较少传递至螺栓2-8的本体部分。如此表示螺栓2-8因螺母的位移所导致的应变与应力,明显集中于螺栓2-8的螺牙。因此,参数超出H4/H3=3/8~1/2的范围的螺栓2-8,恐无法将应变与应力有效传递至螺栓2-8的本体部分,其防松脱与防崩牙的效果恐出现衰退的情形。
请参照图21、图22、图23及图24,为比较标准螺栓与图7的螺栓于θ1=77.5°、82.5°且H4/H3=7/16的参数下的模拟示意图,其中图21为于螺母位移0.15mm时的应变模拟示意图,图22为于螺母位移0.15mm时的应力模拟示意图,图23为于螺母位移0.30mm时的应变模拟示意图,图24为于螺母位移0.30mm时的应力模拟示意图。
图21~图24中,由左至右分别为标准螺栓M10、“θ1=77.5°且H4/H3=7/16的螺栓2-9”与“θ1=82.5°且H4/H3=7/16的螺栓2-10”。于此模拟中,螺母为依照M10JIS标准且螺牙间的牙距为1.5mm的螺母,一个螺母约跨越五个螺牙。
图21与图22说明螺母往下位移0.15mm的情况。如图21所示,螺母约 使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使螺栓2-9及螺栓2-10各自的第一个至第三个螺牙产生有应变的情况。如图22所示,标准螺栓M10约将应力分散至第一个至第三个螺牙,螺栓2-9及螺栓2-10各自约将应力分散至第一个至第五个螺牙。
图23与图24说明螺母往下位移0.30mm的情况。如图23所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使螺栓2-9及螺栓2-10各自的第一个至第三个螺牙产生有应变的情况。如图24所示,标准螺栓M10约将应力分散至第一个至第三个螺牙,螺栓2-9及螺栓2-10各自约将应力分散至第一个至第五个螺牙。
由上可知,相较于标准螺栓M10,各种满足θ1=75°~90°且H4/H3=7/16的参数的螺栓2-9及螺栓2-10各自具有更多螺牙产生有应变的情况,所以有较多个螺牙能产生弹性恢复力以对螺母增加正向力,进而增加摩擦力。因此,满足上述参数的螺栓2-9及螺栓2-10各自可在遭遇震动的过程中达到防止松脱的效果。再者,螺栓2-9及螺栓2-10各自的众螺牙所分担的应力分布较为均匀,所以能分散应力,进而达到防止崩牙的效果。
而且,比较螺母的位移为0.15mm及0.30mm的情况,满足上述参数的螺栓2-9及螺栓2-10各自的螺纹部所产生的应变与所受到的应力皆没有显著变化。因此,在螺母因震动而具有相异的位移时,螺栓2-9及螺栓2-10各自的螺纹部的应变与应力皆未有显著变化,所以螺栓2-9及螺栓2-10各自与螺母的摩擦力也不会有显著变化,而可认为螺栓2-9及螺栓2-10不会受到震动的影响而产生松脱的问题。
请参照图25、图26、图27及图28,为比较标准螺栓与图7的螺栓于θ1=77.5°、82.5°且H4/H3=3/8的参数下的模拟示意图,其中图25为于螺母位移0.15mm时的应变模拟示意图,图26为于螺母位移0.15mm时的应力模拟示意图,图27为于螺母位移0.30mm时的应变模拟示意图,图28为于螺母位移0.30mm时的应力模拟示意图。
图25~图28中,由左至右分别为标准螺栓M10、“θ1=77.5°且H4/H3=3/8的螺栓2-11”与“θ1=82.5°且H4/H3=3/8的螺栓2-12”。于此模拟中,螺母为依照M10JIS标准且螺牙间的牙距为1.5mm的螺母,一个螺母约跨越五个螺牙。
图25与图26说明螺母往下位移0.15mm的情况。如图25所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使螺栓2-11及螺栓2-12各自的第一个至第三个螺牙产生有应变的情况。如图26所示,标准螺栓M10约将应力分散至第一个至第三个螺牙,螺栓2-11及螺栓2-12各自约将应力分散至第一个至第五个螺牙。
图27与图28说明螺母往下位移0.30mm的情况。如图27所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使螺栓2-11及螺栓2-12各自的第一个至第三个螺牙产生有应变的情况。如图28所示,标准螺栓M10约将应力分散至第一个至第三个螺牙,螺栓2-11及螺栓2-12各自约将应力分散至第一个至第五个螺牙。
由上可知,相较于标准螺栓M10,各种满足θ1=75°~90°且H4/H3=3/8的参数的螺栓2-11及螺栓2-12各自具有更多螺牙产生有应变的情况,所以有较多个螺牙能产生弹性恢复力以对螺母增加正向力,进而增加摩擦力。因此,满足上述参数的螺栓2-11及螺栓2-12各自可在遭遇震动的过程中达到防止松脱的效果。再者,螺栓2-11及螺栓2-12各自的众螺牙所分担的应力分布较为均匀,所以能分散应力,进而达到防止崩牙的效果。
而且,比较螺母的位移为0.15mm及0.30mm的情况,满足上述参数的螺栓2-11及螺栓2-12各自的螺纹部所产生的应变与所受到的应力皆没有显著变化。因此,在螺母因震动而具有相异的位移时,螺栓2-11及螺栓2-12各自的螺纹部的应变与应力皆未有显著变化,所以螺栓2-11及螺栓2-12各自与螺母的摩擦力也不会有显著变化,而可认为螺栓2-11及螺栓2-12不会受到震动的影响而产生松脱的问题。
请参照图29,为本申请另一实施例的螺栓的剖面局部放大图。
图29的螺栓4的承重面431的反曲点IP的切线与中心轴CA的夹角θ1为75°~90°,较佳为77.5°~82.5°。牙峰T至牙底B4沿本体41的径向的垂直距离的差异为牙高H7。反曲点IP至本体41的距离H8为牙高H7的3/8~1/2。
图29的螺栓4的非承重面432的连接面432a与承重面431的凹曲面431a拟合于相同的几何曲线OV3。几何曲线OV3具有对称轴SA3。对称轴SA3与牙底B4错开,且对称轴SA3与中心轴CA的夹角θ3为锐角。于本实施例中,几何曲线OV3为椭圆线,但不以此为限。于其他实施例中,几何曲线OV3也 可为双曲线的其中一曲线或拋物线等几何曲线。此外,于其他实施例中,螺栓4的非承重面432的连接面432a与承重面431的凹曲面431a也可拟合于相同的圆弧线。
请参照图30、图31、图32及图33,图30为比较标准螺栓与图29的螺栓于螺母位移0.15mm时的应变模拟示意图,图31为比较标准螺栓与图29的螺栓于螺母位移0.15mm时的应力模拟示意图,图32为比较标准螺栓与图29的螺栓于螺母位移0.30mm时的应变模拟示意图,图33为比较标准螺栓与图29的螺栓于螺母位移0.30mm时的应力模拟示意图。
图30~图33中,由左至右分别为标准螺栓M10与图29的螺栓4。于此模拟中,螺母为依照M10JIS标准且螺牙间的牙距为1.5mm的螺母,一个螺母约跨越五个螺牙。所使用的螺栓4,其H8/H7实质上为0.392,θ1实质上为80.5°。
图30与图31说明螺母往下位移0.15mm的情况。如图30所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使螺栓4的第一个至第五个螺牙产生有应变的情况。如图31所示,标准螺栓M10约将应力分散至第一个至第三个螺牙,螺栓4约将应力分散至第一个至第五个螺牙。
图32与图33说明螺母往下位移0.30mm的情况。如图32所示,螺母约使标准螺栓M10的第一个至第二个螺牙产生有应变的情况,螺母约使螺栓4的第一个至第五个螺牙产生有应变的情况。如图33所示,标准螺栓M10约将应力分散至第一个至第四个螺牙,螺栓4约将应力分散至第一个至第五个螺牙。
由上可知,相较于标准螺栓M10,螺栓4具有更多螺牙产生有应变的情况,所以有较多个螺牙能产生弹性恢复力以对螺母增加正向力,进而增加摩擦力。因此,螺栓4可在遭遇震动的过程中达到防止松脱的效果。再者,螺栓4的众螺牙所分担的应力分布较为均匀,所以能分散应力,进而达到防止崩牙的效果。
而且,比较螺母的位移为0.15mm及0.30mm的情况,螺栓4的螺纹部所产生的应变与所受到的应力皆没有显著变化。因此,在螺母因震动而具有相异的位移时,螺栓4的螺纹部的应变与应力皆未有显著变化,所以螺栓4与螺 母的摩擦力也不会有显著变化,而可认为螺栓4不会受到震动的影响而产生松脱的问题。
综上所述,本申请一实施例的螺栓,螺栓的螺纹部的承重面为斜率连续的面或具有反曲点,且承重面包含相连的凸曲面及凹曲面,凸曲面较凹曲面远离本体,凹曲面触及本体。借此,螺纹部能够于承受力量时顺应地产生形变。如此的螺栓在遭遇震动的过程中,螺纹部的弹性恢复力可对于此螺栓所锁附的元件增加正向力,进而增加摩擦力,以达到防止螺栓松脱的效果。此外,还能够加强螺栓的螺纹部于承受沿螺栓本体中心轴方向的重量负荷时将应力分散的能力,进而达到防止崩牙的效果。
以上所述仅为本申请的实施例而已,并不用于限制本申请。对于本领域技术人员来说,本申请可以有各种更改和变化。凡在本申请的精神和原理之内所作的任何修改、等同替换、改进等,均应包含在本申请的权利要求范围之内。
Claims (20)
- 一种螺栓,其特征在于,该螺栓包括:一本体,具有一中心轴;一头部,设置于该本体的一端;以及一螺纹部,沿该中心轴螺旋围绕且连接于该本体,该螺纹部具有一承重面朝向该头部,该承重面为一斜率连续的面,该承重面包括一凹曲面、一凸曲面及一承重牙腹面,该凹曲面触及该本体,该凸曲面较该凹曲面远离该本体,该凸曲面的一侧与该凹曲面相连且该凸曲面的另一侧与该承重牙腹面相连。
- 如权利要求1所述的螺栓,其中,该凸曲面与该凹曲面的交接处的一切线与该中心轴的夹角为75°~90°。
- 如权利要求2所述的螺栓,其中,该凸曲面与该凹曲面的交接处的一切线与该中心轴的夹角为77.5°~82.5°。
- 如权利要求1所述的螺栓,其中,该螺纹部至该本体的最远距离为一牙高,该凸曲面与该凹曲面的交接处的至该本体的距离为该牙高的3/8~1/2。
- 如权利要求4所述的螺栓,其中,该凸曲面与该凹曲面的交接处的一切线与该中心轴的夹角为75°~90°。
- 如权利要求1所述的螺栓,其中,该螺纹部更具有一非承重面,该非承重面背向该头部,该非承重面包括一连接面及一非承重牙腹面,该连接面的一侧触及该本体且该连接面的另一侧与该非承重牙腹面相连,该凹曲面拟合于一第一几何曲线,该连接面拟合于一第二几何曲线,该第一几何曲线相异于该第二几何曲线,该承重面至该中心轴的投影长度等于或小于该非承重面至该中心轴的投影长度。
- 如权利要求6所述的螺栓,其中,该凸曲面与该凹曲面的交接处的一切线与该中心轴的夹角为75°~90°,该螺纹部至该本体的最远距离为一牙高,该凸曲面与该凹曲面的交接处的至该本体的距离为该牙高的3/8~1/2。
- 如权利要求6所述的螺栓,其中,该第一几何曲线具有一第一对称轴,该第二几何曲线具有一第二对称轴,该第一对称轴及该第二对称轴实质上垂直于该中心轴,该第一对称轴及该第二对称轴重合。
- 如权利要求1所述的螺栓,其中,该螺纹部更具有一非承重面,该非承重面背向该头部,该非承重面包括一连接面及一非承重牙腹面,该连接面的一 侧触及该本体且该连接面的另一侧与该非承重牙腹面相连,该连接面及该凹曲面拟合于相同的一几何曲线,该承重面至该中心轴的投影长度等于或小于该非承重面至该中心轴的投影长度。
- 如权利要求9所述的螺栓,其中,该凸曲面与该凹曲面的交接处的一切线与该中心轴的夹角为75°~90°,该螺纹部至该本体的最远距离为一牙高,该凸曲面与该凹曲面的交接处的至该本体的距离为该牙高的3/8~1/2。
- 一种螺栓,其特征在于,该螺栓包括:一本体,具有一中心轴;一头部,设置于该本体的一端;以及一螺纹部,沿该中心轴螺旋围绕且连接于该本体,该螺纹部具有一承重面朝向该头部,该承重面具有一反曲点,该承重面包括一凹曲面、一凸曲面及一承重牙腹面,该凹曲面触及该本体,该凸曲面较该凹曲面远离该本体,该凸曲面的一侧经由该反曲点与该凹曲面相连且该凸曲面的另一侧与该承重牙腹面相连。
- 如权利要求11所述的螺栓,其中,该反曲点的一切线与该中心轴的夹角为75°~90°。
- 如权利要求12所述的螺栓,其中,该反曲点的一切线与该中心轴的夹角为77.5°~82.5°。
- 如权利要求11所述的螺栓,其中,该螺纹部至该本体的最远距离为一牙高,该反曲点至该本体的距离为该牙高的3/8~1/2。
- 如权利要求14所述的螺栓,其中,该反曲点的一切线与该中心轴的夹角为75°~90°。
- 如权利要求11所述的螺栓,其中,该螺纹部更具有一非承重面,该非承重面背向该头部,该非承重面包括一连接面及一非承重牙腹面,该连接面的一侧触及该本体且该连接面的另一侧与该非承重牙腹面相连,该凹曲面拟合于一第一几何曲线,该连接面拟合于一第二几何曲线,该第一几何曲线相异于该第二几何曲线,该承重面至该中心轴的投影长度等于或小于该非承重面至该中心轴的投影长度。
- 如权利要求16所述的螺栓,其中,该反曲点的一切线与该中心轴的夹角为75°~90°,该螺纹部至该本体的最远距离为一牙高,该反曲点至该本体的 距离为该牙高的3/8~1/2。
- 如权利要求16所述的螺栓,其中,该第一几何曲线具有一第一对称轴,该第二几何曲线具有一第二对称轴,该第一对称轴及该第二对称轴实质上垂直于该中心轴,该第一对称轴及该第二对称轴重合。
- 如权利要求11所述的螺栓,其中,该螺纹部更具有一非承重面,该非承重面背向该头部,该非承重面包括一连接面及一非承重牙腹面,该连接面的一侧触及该本体且该连接面的另一侧与该非承重牙腹面相连,该连接面及该凹曲面拟合于相同的一几何曲线,该承重面至该中心轴的投影长度等于或小于该非承重面至该中心轴的投影长度。
- 如权利要求19所述的螺栓,其中,该反曲点的一切线与该中心轴的夹角为75°~90°,该螺纹部至该本体的最远距离为一牙高,该反曲点至该本体的距离为该牙高的3/8~1/2。
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- 2018-10-31 US US16/496,074 patent/US11313401B2/en active Active
- 2018-10-31 EP EP18909268.7A patent/EP3667109A4/en active Pending
- 2018-10-31 WO PCT/CN2018/113010 patent/WO2020087347A1/zh unknown
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Also Published As
Publication number | Publication date |
---|---|
EP3667109A1 (en) | 2020-06-17 |
EP3667109A4 (en) | 2020-11-11 |
US11313401B2 (en) | 2022-04-26 |
US20200224703A1 (en) | 2020-07-16 |
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