Internal supporting type anti-loosening nut

Abstract

The utility model provides an inner supporting type anti-loosening nut, and relates to the field of mechanical fasteners. Comprising a locking nut and a fastening nut. One end face of the fastening nut is an inclined face and inclines towards the opposite end face. The inclined face is provided with an inverted-cone-shaped counter bore concentric with the threaded hole, and the caliber of the inverted-cone-shaped counter bore is gradually increased from outside to inside. One end face of the locking nut is provided with a cylindrical boss which is concentric with the threaded hole of the locking nut and is communicated with the threaded hole. The outer diameter of the cylindrical boss is matched with the minimum caliber of the inverted-cone-shaped counter bore. The inclination angle of the inclined face is larger than that of the inner wall of the inverted-cone-shaped counter bore. During use, the fastening nut is screwed on the bolt firstly, and then the cylindrical boss of the locking nut faces the inverted conical counter bore of the fastening nut and is screwed on the bolt in an overlapped mode. The structure is simple and manufacturing is easy; compared with the prior art, the anti-loosening nut has the advantages that the influence on metal fatigue strength of the nut hole wall is weak, generated stress is relatively dispersed, the service life of the nut can be greatly prolonged, and meanwhile, the long-time anti-loosening capacity of the nut is improved due to the arrangement of the tenon structure.

Description

Technical Field

[0001] The utility model relates to the field of mechanical fasteners, in particular to an internally supported anti-loosening nut. Background Art

[0002] In the field of mechanical fastening, bolts are usually fastened with nuts to prevent them from loosening during operation. However, due to the vibrations of most mechanical equipment, conventional nuts are prone to loosening. Therefore, it is necessary to use anti-loosening nuts and anti-loosening washers that match the nuts.

[0003] However, existing anti-loosening nuts generally have the problem of high production costs, poor long-term anti-loosening effect, and a certain gap between the comprehensive use effect and test results and the existing non-loosening nuts. Therefore, non-loosening nuts are widely used in various industries and various important projects and equipment.

[0004] However, this type of nut that never loosens still has some defects during use: when used in some situations with a high safety factor, the nut needs to be tightened again after a period of use, and it is easy to break due to metal fatigue, resulting in the need for replacement after a certain period of use, which has a high cost of use; and the manufacturing material and processing precision requirements of the nut are both high, so the manufacturing cost is also high. Utility Model Content

[0005] The purpose of the utility model is to provide an internal support anti-loosening nut with a simple structure and easy manufacturing; it has a weak effect on the metal fatigue strength of the nut hole wall, and the stress generated is relatively dispersed, which can greatly improve the service life of the nut while having a longer anti-loosening effect.

[0006] The embodiment of the present utility model is achieved as follows:

[0007] The embodiment of the present application provides an internal support anti-loosening nut, which includes a locking nut and a fastening nut, wherein the locking nut and the fastening nut are both provided with a threaded hole for a bolt to pass through; one end surface of the fastening nut is inclined toward its opposite end surface; the inclined surface is provided with an inverted conical countersunk hole that is concentric with the threaded hole and has a diameter that gradually increases from the outside to the inside;

[0008] One end surface of the locking nut is provided with a cylindrical boss which is concentric with and interpenetrating the threaded hole; the outer diameter of the cylindrical boss is adapted to the minimum diameter of the inverted conical countersunk hole; wherein the inclination angle of the inclined surface is greater than the inclination angle of the inner wall of the inverted conical countersunk hole;

[0009] When in use, the fastening nut is first tightened onto the bolt, and then the cylindrical boss of the locking nut is overlapped and tightened onto the bolt toward the inverted conical countersunk hole of the fastening nut.

[0010] Furthermore, based on the aforementioned solution, the depth of the inverted tapered countersunk hole is greater than the length of the cylindrical boss.

[0011] Furthermore, based on the aforementioned scheme, when the locking nut is tightened, one side wall of the cylindrical boss matches the inner wall of the inverted conical countersunk hole on the higher side of the inclined surface, and there is a locking gap between part of the end surface on the lower side of the inclined surface and the end face of the locking nut.

[0012] Furthermore, based on the aforementioned solution, the inclination angle of the above-mentioned inclined surface is 3°-16°, and the inclination angle of the inner wall of the inverted cone-shaped countersunk hole is 1°-14°.

[0013] Furthermore, based on the aforementioned solution, the bolts are made of a material with a certain elastic deformation.

[0014] Compared with the prior art, the embodiments of the present invention have at least the following advantages or beneficial effects:

[0015] The present invention provides a locking nut and a fastening nut, and designs one end face of the fastening nut as an inclined surface. When in use, the fastening nut is first tightened on the bolt, and the inclined surface is turned away from the part to be tightened, and then the locking nut is overlapped and locked on the inclined surface of the fastening nut. The double nut locking force is greater. At the same time, due to the existence of the inclined surface, the bolt will bend toward the inclined surface during the locking process of the locking nut, generating elastic deformation, thereby causing the locking nut to be stressed toward the inclined side, so that its internal thread is tightly engaged with the external thread of the bolt, thereby making it less likely to loosen. By opening a hole with a diameter of The inverted conical countersunk hole gradually increases from the outside to the inside, and a cylindrical boss is set on one end face of the locking nut, that is, the inner wall of the inverted conical countersunk hole of the fastening nut is also inclined, and its inclination angle is smaller than the inclination angle of the inclined surface. In this way, when the cylindrical boss of the fastening nut is inserted into the inverted conical countersunk hole, the cylindrical boss is also tilted, forming a tenon structure with the inverted conical countersunk hole. When the locking nut is further tightened, the side wall of the cylindrical boss will squeeze the inner wall of the inverted conical countersunk hole, so that the fastening nut is subjected to force toward the high point of the inclined surface, which is opposite to the force direction of the locking nut, so that the two are engaged in opposite directions on the bolt, further enhancing the anti-loosening effect. The structure of the present application is simple and easy to manufacture; it has a weak effect on the metal fatigue strength of the nut hole wall, and the stress generated is relatively dispersed, which can greatly improve the service life of the nut; at the same time, because a tenon structure is set, the anti-loosening ability of the nut is improved for a long time. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following is a brief introduction to the drawings required for use in the embodiments. It should be understood that the following drawings only illustrate certain embodiments of the present invention and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other relevant drawings can be obtained based on these drawings without paying any creative work.

[0017] Figure 1 This is a structural diagram of an internally supported anti-loosening nut in an initial state according to an embodiment of the present invention;

[0018] Figure 2 This is a structural diagram of an internal support type anti-loosening nut in a tightened state according to an embodiment of the present invention;

[0019] Figure 3 This is a top view of an internally supported anti-loosening nut according to an embodiment of the present invention.

[0020] Icons: 1-locking nut, 2-fastening nut, 21-inclined surface, 22-inverted tapered countersunk hole, 3-bolt, 11-cylindrical boss, 4-locking gap, 5-vacant cavity, 6-pressing piece. DETAILED DESCRIPTION

[0021] The inventors have found through analysis of the prior art that the existing never-loosening nuts have the following three main defects:

[0022] 1. In some applications requiring a higher safety factor, this nut needs to be tightened again every six months or a certain period of time. This operation is called re-tightening. The reason is that this nut is not designed with a special structure to prevent loosening due to axial vibration. This will greatly reduce the cost and convenience of use if there are many nuts or the installation location is not convenient for re-tightening.

[0023] 2. Due to its structural design, the nut's tapered portion and the spherical hole on the upper thread are subjected to significant compressive pressure after tightening. This is especially true if the tapered portion cannot be designed to be excessively thick. This can lead to the nut breaking after reaching a certain level of metal fatigue strength. Therefore, when using this nut on equipment requiring high safety factors, it must be replaced within a certain period of time, even if it is not broken. This results in a relatively high cost of using this nut.

[0024] 3. The production process of this type of nut requires very high steel materials, heat treatment technology and processing precision. Therefore, the price is high and it is difficult to popularize.

[0025] The embodiments of the present application are described in detail below in conjunction with the drawings in the embodiments of the present application.

[0026] Please refer to Figure 1-Figure 3 , shown is the overall structural diagram of the internal support anti-loosening nut,

[0027] This embodiment provides an internally supported anti-loosening nut, comprising:

[0028] The locking nut 1 and the fastening nut 2 are each provided with a threaded hole for the bolt 3 to pass through; one end face of the fastening nut 2 is formed into an inclined surface 21 and is inclined toward its opposite end face; the inclined surface 21 is provided with an inverted conical countersunk hole 22 which is concentric with the threaded hole and has a diameter that gradually increases from the outside to the inside;

[0029] One end face of the locking nut 1 is provided with a cylindrical boss 11 which is concentric with and interpenetrating the threaded hole. The outer diameter of the cylindrical boss 11 is adapted to the minimum diameter of the inverted conical counterbore 22. The inclination angle of the inclined surface 21 is greater than the inclination angle of the inner wall of the inverted conical counterbore 22.

[0030] When in use, first tighten the fastening nut 2 onto the bolt 3 , and then tighten the cylindrical boss 11 of the locking nut 1 onto the bolt 3 with the side facing the inverted conical countersunk hole 22 .

[0031] Next, an internally supported anti-loosening nut according to this exemplary embodiment will be further described.

[0032] In some embodiments, reference Figure 1-Figure 3 The locking nut 1 and the fastening nut 2 are both provided with threaded holes for the bolt 3 to pass through. When in use, the locking nut 1 and the fastening nut 2 overlap and are fastened to the bolt 3. One end face of the fastening nut 2 is formed into an inclined surface 21 and is inclined toward its opposite end face. When in use, the fastening nut 2 is first fastened to the bolt 3, with the inclined surface 21 facing away from the part to be compressed 6, so that when the locking nut 1 and the fastening nut 2 overlap, one end face of the locking nut 1 abuts against the inclined surface 21. In this way, when the locking nut 1 is tightened with the fastening nut 2, after contacting the high point of the inclined surface 21 of the fastening nut 2, the locking nut 1 is continuously tightened, which can cause the locking nut 1 to tilt to one side in the inclined direction, thereby generating a force that elastically deforms the bolt 3. The elastic deformation of the bolt 3 generates a reaction force in the inclined direction on the locking nut 1, causing the helical line of the locking nut 1 to move downward along the helical line of the bolt 3 and tightly engage with the thread of the bolt 3.

[0033] It should be noted that the high point of the inclined surface 21 acts like a fulcrum, forcing the bolt 3 to bend to one side. By setting the angle of the inclined surface 21, the bolt 3 can be controlled to deform elastically without plastic deformation.

[0034] In a specific embodiment, if Figure 2As shown, when the lower plane of the locking nut 1 and the upper inclined surface of the fastening nut 2 are partially or completely in contact with each other, the entire bolt 3 generates a huge elastic deformation force, causing the locking nut 1 to be subjected to a force F1 to the right and tightly squeezed on the bolt 3, achieving a good anti-loosening effect.

[0035] In some embodiments, the inclined surface 21 is provided with an inverted conical countersunk hole 22 that is concentric with the threaded hole and has a diameter that gradually increases from the outside to the inside. That is, the inclined surface 21 is provided with an inverted inverted conical countersunk hole 22, the diameter of the outer end surface is smaller than the diameter of the inner end surface, and the inner wall of the inverted conical countersunk hole 22 is inclined. One end surface of the locking nut 1 is provided with a cylindrical boss 11 that is concentric with the threaded hole and interpenetrates the threaded hole. The outer diameter of the cylindrical boss 11 is adapted to the minimum diameter of the inverted conical countersunk hole 22, so that the cylindrical boss 11 can be snapped into the inverted conical countersunk hole 22. The inclined inner wall of the inverted conical countersunk hole 22 causes the cylindrical boss 11 to gradually tilt during the process of being snapped into its groove. The cylindrical boss 11 and the inverted conical countersunk hole 22 form a tenon structure, which can effectively connect the two nuts and reduce the axial rotational displacement of the nut to a certain extent.

[0036] The inclination angle of the inclined surface 21 is designed to be greater than the inclination angle of the inner wall of the inverted conical countersunk hole 22. In the process of gradually tightening the locking nut 1, the bolt 3 gradually bends toward the inclination direction of the inclined surface 21, and the cylindrical boss 11 gradually tilts synchronously, and its outer wall on the high point side of the inclined surface 21 contacts the inner wall of the inverted conical countersunk hole 22. Then, the locking nut 1 is continuously tightened, and the side wall of the cylindrical boss 11 will squeeze the inner wall of the inverted conical countersunk hole 22, thereby causing the fastening nut 2 to be subjected to an F2 force toward the high point of the inclined surface 21, which is opposite to the F1 force subjected to the locking nut 1. The two forces in opposite directions cause it to bite on the bolt 3 from two different directions, thereby effectively coping with the loosening effect of lateral vibration on the nut, and effectively preventing the locking nut 1 and the fastening nut 2 from loosening during long-term vibration, thereby overcoming the design defects of the existing nuts that never loosen. At the same time, the cylindrical boss 11 squeezes the inverted conical countersunk hole 22 to form an internal support structure from the inside to the outside, which has a weak effect on the metal fatigue strength of the extruded nut hole wall and the generated stress is relatively dispersed, thereby improving the service life.

[0037] As a preferred embodiment, the depth of the above-mentioned inverted conical countersunk hole 22 is greater than the length of the cylindrical boss 11, so that the locking nut 1 can partially or completely fit with the fastening nut 2, and after the locking nut 1 is locked, there is a vacant cavity 5 between the cylindrical boss 11 and the inverted conical countersunk hole 22 to achieve stable locking while reserving space for supplementary force, that is, space for re-locking.

[0038] As a preferred embodiment, when the lock nut 1 is tightened, a sidewall of the cylindrical boss 11 mates with the inner wall of the inverted tapered counterbore 22 on the higher side of the inclined surface 21, leaving a locking gap 4 between a portion of the end surface on the lower side of the inclined surface 21 and the end face of the lock nut 1. This locking gap 4 and the vacant cavity 5 both provide space for additional force, ensuring that the lock nut 1 can be continuously tightened, facilitating use in certain specific situations.

[0039] In a preferred embodiment, the angle α1 of the inclined surface 21 is 3°-16°, and the angle α2 of the inner wall of the inverted tapered countersunk hole 22 is 1°-14°. Different angles can be selected based on the material of the bolt 3, with larger angles being preferred for materials with greater strength and elasticity. The angle of the inclined surface 21 is typically 2°-4° greater than the angle of the inner wall of the inverted tapered countersunk hole 22. This allows the hole wall to be held in place while preventing excessive tension that could damage the wall, providing a certain degree of restraint.

[0040] As a preferred embodiment, the bolt 3 is made of a material with a certain elastic deformation. The material of the ordinary bolt 3 or nut has a certain elastic deformation. Compared with permanent anti-loosening nuts, it does not require the use of special high-quality steel, which can save manufacturing costs.

[0041] In a specific embodiment, the bolt 3 is passed through the pressing member 6, and the fastening nut 2 is screwed onto the bolt 3 to achieve the specified pre-tightening force; the locking nut 1 is put on the bolt 3 and the locking nut 1 is screwed toward one end of the fastening nut 2. At this time, the bolt 3 is tightened as shown in FIG. Figure 2 The locking nut 1 is gradually tilted to the right until the side wall of the cylindrical boss 11 contacts the inner wall of the inverted conical countersunk hole 22 to form a tenon structure; continue to tighten the locking nut 1, the cylindrical boss 11 squeezes the inner wall of the inverted conical countersunk hole 22, and the locking nut 1 is tightened to Figure 2 When the lock nut 1 is in the correct position, the installation work is completed. At this moment, the locking gap 4 and the vacant cavity 5 can ensure that the lock nut 1 can be continuously tightened.

[0042] It should be noted that grease can be injected into the inverted conical countersunk hole 22 of the fastening nut 2 during installation to prevent the nut from corroding from the inside due to environmental problems, thereby increasing the service life.

[0043] Beneficial effects of the embodiments of the present application:

[0044] 1. Simple structure and easy to manufacture.

[0045] 2. Easy to install and disassemble, no additional auxiliary tools are required.

[0046] 3. Once installed, it can prevent loosening for a long time and basically does not require excessive maintenance and subsequent tightening work.

[0047] 4. Compared with the existing rigid extrusion structure that never loosens nuts, the internal support structure of this design has a weaker effect on the metal fatigue strength of the nut hole wall, and the generated stress is relatively dispersed. This will correspondingly increase the service life of the nut, reduce the requirements for material selection, and reduce production costs.

[0048] 5. The locking nut 1 and the fastening nut 2 are subjected to forces in opposite directions, effectively preventing the loosening of the nuts caused by lateral vibration. At the same time, the tenon structure can effectively connect the two nuts and reduce the rotational displacement of the axial nuts to a certain extent.

[0049] In addition, unless otherwise expressly specified or limited, in the embodiments of the present application, if the terms "installation" and "connection" appear, they should be understood in a broad sense. For example, "connection" can be a detachable connection or a non-detachable connection; it can be a direct connection or an indirect connection through an intermediate medium. If the terms "upper", "lower", "left", "right", "inside", "outside", "side" and other directional terms appear, they are only with reference to the direction of the accompanying drawings or the orientation in which the product is usually placed when in use. They are only for the purpose of clearly describing the present application, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and cannot be understood as a limitation on the present application. The terms "first", "second", etc. are only used to distinguish the description and cannot be understood as indicating or implying relative importance; "multiple" means at least two. In the embodiments of the present application, the limitations of relative positional relationships such as parallel, perpendicular, aligned, etc. mentioned are all based on the current technological level, and are not absolutely strict limitations. A small amount of deviation is allowed, and approximately parallel, approximately perpendicular, approximately aligned, etc. are all acceptable. For example, A and B are parallel, which means that A and B are parallel or approximately parallel, and the angle between A and B can be between 0 degrees and 10 degrees.

[0050] The above are only some of the embodiments and implementation methods of the present application. The scope of protection of the present application is not limited to these. In the absence of conflict, the embodiments and features in the embodiments of the present application can be combined with each other. Any combination of features in different embodiments is also within the scope of protection of the present application. Any changes or replacements that can be easily thought of by any technician familiar with the field within the technical scope disclosed in the present application should be covered by the scope of protection of the present application.

Claims

1. An internal support anti-loosening nut, characterized in that: The invention comprises a locking nut and a fastening nut, wherein the locking nut and the fastening nut are both provided with a threaded hole for passing a bolt; one end face of the fastening nut is inclined toward its opposite end face; the inclined face is provided with an inverted conical countersunk hole which is concentric with the threaded hole and has a diameter which increases gradually from the outside to the inside; One end surface of the locking nut is provided with a cylindrical boss which is concentric with and interpenetrating the threaded hole; the outer diameter of the cylindrical boss is adapted to the minimum diameter of the inverted conical countersunk hole; wherein the inclination angle of the inclined surface is greater than the inclination angle of the inner wall of the inverted conical countersunk hole; When in use, the fastening nut is first tightened onto the bolt, and then the cylindrical boss of the locking nut is overlapped and tightened onto the bolt toward one side of the inverted conical countersunk hole.

2. The internal support anti-loosening nut according to claim 1, characterized in that: The depth of the inverted tapered countersunk hole is greater than the length of the cylindrical boss.

3. The internal support anti-loosening nut according to claim 2, characterized in that: When the locking nut is tightened, a side wall of the cylindrical boss matches the inner wall of the inverted conical countersunk hole on the higher side of the inclined surface, and a locking gap exists between a portion of the end surface on the lower side of the inclined surface and the end surface of the locking nut.

4. The internal support anti-loosening nut according to claim 1, characterized in that: The inclination angle of the inclined surface is 3°-16°, and the inclination angle of the inner wall of the inverted cone-shaped countersunk hole is 1°-14°.

5. The internal support anti-loosening nut according to claim 1, characterized in that: The bolt is made of a material with a certain elastic deformation.

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