CN218625002U

CN218625002U - Slope-shaped self-locking fastener

Info

Publication number: CN218625002U
Application number: CN202222816150.2U
Authority: CN
Inventors: 王静怡; 寻凯; 朱恺; 方亮; 王振华
Original assignee: Tianhong Power Technology Yangzhou Co ltd
Current assignee: Tianhong Power Technology Yangzhou Co ltd
Priority date: 2022-10-25
Filing date: 2022-10-25
Publication date: 2023-03-14
Anticipated expiration: 2032-10-25

Abstract

The application discloses a slope-shaped self-locking fastener which comprises a bolt, a nut and a gasket; the gasket is suitable for being sleeved on the bolt and is positioned between the bolt and the nut; the relative terminal surface of gasket and nut is suitable for and cooperates through the slope shape structure to make the nut drive the gasket and rotate until and tight around the bolt jointly, and then the slope shape structure locks the nut through producing along radial resultant moment. The beneficial effect of this application: through increase the gasket between nut and bolt to cooperate through the slope shape structure between gasket and the nut, thereby when nut and bolt go on and tightly, realize the auto-lock through producing radial moment of couple to the nut. The slope-shaped self-locking fastener can meet the self-locking requirements of nuts of all specifications on all occasions, does not damage threads, can realize repeated detachable connection of the threads, and is adjustable in locking torque and reliable in self-locking.

Description

Slope-shaped self-locking fastener

Technical Field

The application relates to the technical field of fasteners, in particular to a slope-shaped self-locking fastener.

Background

Nut self-locking has great requirements in various industries. The existing nut self-locking methods include a thread-destroying backstop method, an axial friction couple moment self-locking method, a radial friction couple moment self-locking method and the like. All the methods are realized by performing structural design on the nut structure, so that the manufacturing structure of the nut is easy to be complicated, and further the manufacturing cost is increased; or the structure of the nut is damaged, and the nut cannot be repeatedly used.

SUMMERY OF THE UTILITY MODEL

One of the objects of the present application is to provide a ramp-shaped self-locking fastener that is simple to manufacture and can be reused.

In order to achieve at least one of the above purposes, the technical solution adopted by the present application is: a slope-shaped self-locking fastener comprises a bolt, a nut and a gasket; the gasket is suitable for being sleeved on the bolt and is positioned between the bolt and the nut; the opposite end surfaces of the gasket and the nut are suitable for being matched through a slope-shaped structure, so that the nut drives the gasket to rotate around the bolt together until the gasket is tightened, and then the slope-shaped structure locks the nut by generating a resultant moment in the radial direction.

Preferably, the slope-shaped structure comprises a first extrusion surface and a second extrusion surface; the first extrusion surface and the second extrusion surface are obliquely arranged and have the same inclination angle; the first extrusion surface and the second extrusion surface are respectively arranged on the opposite end surfaces of the nut and the gasket, so that when the nut and the bolt are fastened together, the first extrusion surface and the second extrusion surface self-lock the nut through component force in the radial direction.

Preferably, the included angle between the first pressing surface and the radial plane and the included angle between the second pressing surface and the radial plane are larger than the friction angle between the contact surfaces of the nut and the gasket.

Preferably, the opposite end surfaces of the nut and the gasket are both obliquely arranged to form the first pressing surface and the second pressing surface, respectively.

Preferably, the outer contour of the gasket is in a regular hexagon shape, and the outer contour size of the gasket is the same as that of the nut; the starting point and the end point of the first pressing surface and the second pressing surface are both located at the positions of the maximum radial dimensions of the nut and the gasket.

Preferably, the opposite end surfaces of the nut and the gasket are respectively provided with at least one lug and a groove; when the nut and the bolt are tightly combined, the nut is suitable for driving the gasket to synchronously rotate until the gasket is tightly combined through the clamping of the convex block and the groove; the first extrusion surface is arranged on the lug, and the second extrusion surface is arranged on the groove.

Preferably, the first extrusion surface and the second extrusion surface are respectively arranged at the top end of the bump and the bottom end of the groove; or the first extrusion surface and the second extrusion surface are respectively arranged on the side edges of the lug and the groove along the circumferential direction.

Preferably, a second through hole is formed in the center of the gasket, the diameter of the second through hole is D, and the major diameter of the thread of the bolt is D; D-D is less than or equal to 0.4mm.

Preferably, a first through hole is formed in the center of one end, close to the gasket, of the nut, the first through hole and the second through hole are identical in size, and the axes of the first through hole and the threaded hole of the nut are aligned.

Preferably, the slope-shaped self-locking fastener further comprises a spring pad, and the spring pad is suitable for being sleeved on the bolt, so that when the nut and the bolt are fastened together, the spring pad is suitable for being elastically abutted against one end, far away from the nut, of the gasket.

Compared with the prior art, the beneficial effect of this application lies in:

(1) Through increase the gasket between nut and bolt to cooperate through the slope shape structure between gasket and the nut, thereby when nut and bolt go on and tight, realize the auto-lock through producing radial moment of couple to the nut.

(2) The slope-shaped self-locking fastener can meet the self-locking requirements of nuts of all specifications on all occasions, does not damage threads, can realize repeated detachable connection of the threads, and is adjustable in locking torque and reliable in self-locking.

Drawings

Fig. 1 is a schematic cross-sectional structural view of one embodiment of the present invention.

Fig. 2 is a schematic structural view of the nut shown in fig. 1 according to the present invention.

Fig. 3 is a schematic structural view of the gasket according to the embodiment of fig. 1 of the present invention.

Fig. 4 is a schematic diagram of a stress state when the embodiment of fig. 1 of the present invention is tightened.

Fig. 5 is a schematic cross-sectional structure diagram of another embodiment of the present invention.

Fig. 6 is a schematic partial sectional view of the nut shown in fig. 5 according to the embodiment of the present invention.

Fig. 7 is a schematic top view of the nut shown in fig. 5 according to the present invention.

Fig. 8 is a schematic partial sectional view of the gasket according to the embodiment of the present invention shown in fig. 5.

Fig. 9 is a schematic top view of the gasket shown in fig. 5 according to the embodiment of the present invention.

Fig. 10 is a schematic diagram of the force state of the embodiment of fig. 5 during tightening.

Fig. 11 is a schematic view of the axial self-locking stress state of the present invention.

In the figure: the bolt 100, the nut 200, the threaded hole 210, the first through hole 220, the first pressing surface 230, the projection 240, the gasket 300, the second through hole 310, the second pressing surface 320, the groove 330, and the spring washer 400.

Detailed Description

The present application is further described below with reference to specific embodiments, and it should be noted that, without conflict, any combination between the embodiments described below or between the technical features may form a new embodiment.

In the description of the present application, it should be noted that, for the terms of orientation, such as "central", "lateral", "longitudinal", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc., indicate orientations and positional relationships based on the orientations or positional relationships shown in the drawings, which are only for convenience of description and simplification of the description, but 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 should not be construed as limiting the specific scope of the present application.

It is noted that the terms first, second and the like in the description and in the claims of the present application are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order.

In one preferred embodiment of the present application, as shown in fig. 1 to 11, a ramp-shaped self-locking fastener includes a bolt 100, a nut 200, and a washer 300. Washer 300 may be installed over bolt 100 in a sleeved manner, with washer 300 installed between bolt 100 and nut 200. The opposite end surfaces of the washer 300 and the nut 200 may be engaged by a slope structure, so that the nut 200 drives the washer 300 to rotate together around the bolt 100 until the nut 200 and the bolt 100 are tightened, and the nut 200 and the washer 300 may be locked by a radial resultant torque generated by the slope structure.

It will be appreciated that during the tightening of nut 200 and bolt 100, washer 300 is first slipped onto bolt 100 and then nut 200 and bolt 100 are torqued together. In the process of screwing the nut 200, the washer 300 and the nut 200 need to be aligned by a slope structure, and then the washer 300 and the nut 200 are driven to rotate together by a tool such as a wrench, so as to avoid the interference of the washer 300 on the independent rotation of the nut 200.

In the present embodiment, as shown in fig. 2 to 4 and 6 to 10, the slope structure includes a first pressing surface 230 and a second pressing surface 320; the first pressing surface 230 and the second pressing surface 320 are both inclined at the same angle. First pressing surface 230 and second pressing surface 320 are respectively provided at opposite end surfaces of nut 200 and washer 300, so that when nut 200 and bolt 100 are tightened, first pressing surface 230 and second pressing surface 320 self-lock nut 200 by a component force in a radial direction.

It can be understood that, in the screwing process of the nut 200 and the bolt 100, the washer 300 is firstly pulled until the second pressing surface 320 is attached to the first pressing surface 230 of the nut 200, and then the washer 300 and the nut 200 are simultaneously clamped by a wrench to ensure that the nut 200 and the washer 300 synchronously rotate until the nut 200 is tightened by the washer 300 and the bolt 100.

At this time, the nut 200 and the washer 300 are subjected to a force analysis.

As shown in fig. 4 and 10, the pressing forces generated by the first pressing surface 230 and the second pressing surface 320 pressing each other are equally opposite and perpendicular to the first pressing surface 230 and the second pressing surface 320. The pressing force between the first pressing surface 230 and the second pressing surface 320 is divided, and a first component force in the axial direction and a second component force in the radial direction can be obtained.

Wherein, the first component force can drive the nut 200 and the bolt 100 to axially tighten until the resultant force of the first component force and the supporting force N of the head of the bolt 100 to the gasket 200 _Shaft And (6) balancing. At this time, the threaded axial gap between nut 200 and bolt 100 is eliminated, so that self-locking of nut 200 can be achieved by increasing the frictional force of the contact surfaces generated by the threaded engagement of nut 200 and bolt 100.

The second component of force can drive the washer 300 and the nut 200 to move in the opposite directions a and B, respectively, until the resultant force of the second component of force and the bolt 100 balance the supporting force of the nut 200 and the washer 300, respectively. At this time, positive pressure of washer 300 on bolt 100 is N _A The positive pressure of the nut 200 on the bolt 100 is N _B Positive pressure N _A And N _B Are equal in sizeThe direction is opposite. Due to positive pressure N _A And N _B The positions in the axial direction of the bolt 100 are different so that the positive pressure N is applied _A And N _B A moment that causes the nut 200 and the washer 300 to overturn can be generated in the axial plane of the bolt 100 to further improve the self-locking effect of the nut 200.

As shown in FIG. 11, when the bolt 100 is in use, a moment M is generated to loosen the nut 200 due to vibration and the like _{Pine needle} So that the nut 200 generates a movement tendency toward the loosening direction, the positive pressure N _A And N _B The generated friction torque M _A And M _B Just can be mixed with M _{Pine needle} And reversely, the nut 200 can be prevented from loosening, so that the self-locking of the nut 200 can be further improved.

In this embodiment, as shown in fig. 2 to 4 and fig. 6, 8 and 10, the first pressing surface 230 and the second pressing surface 320 form an angle α with the radial plane, and the value of α is greater than the friction angle of the contact surface between the nut 200 and the washer 300.

It will be appreciated that when nut 200 is tightened with bolt 100, nut 200 and washer 300 are press-fitted via first pressing surface 230 and second pressing surface 320. When the nut 200 tends to be loosened, the nut 200 tends to be rotated spirally with respect to the washer 300 due to the inclined arrangement of the first pressing surface 230 and the second pressing surface 320.

Therefore, the friction angle of the nut 200 self-locking relative to the gasket 300 can be obtained by analyzing the stress between the nut 200 and the gasket 300. Therefore, in order to ensure that the nut 200 can have sufficient self-locking performance, the inclination angle of the first pressing surface 230 and the second pressing surface 320 may be set to be greater than the friction angle of the nut 200 with respect to the washer 300.

It will also be appreciated that the positive pressure N is determined by the force analysis process described above _A And N _B The values of (a) are all related to the included angle alpha; i.e. the larger the angle alpha, the positive pressure N _A And N _B The larger the value of (A) and the smaller the opposite. Therefore, according to the application of the fastener in different working environments, the magnitude of the self-locking torque of the nut 200 can be adjusted by changing the value of the included angle alpha.

In this embodiment, the outer contour of the spacer 300 may be a regular polygon with an even number of sides, and the distance between one pair of opposite sides of the spacer 300 is equal to the distance between any pair of sides of the nut 200. So as to ensure that the washer 300 and the nut 200 are engaged, the washer 300 and the nut 200 can be rotated together by a wrench.

It will be appreciated that the washer 300 is capable of co-movement with the nut 200 in order to ensure that the nut 200 is threaded along the bolt 100. It is necessary to restrain the washer 300 by a tool to prevent the washer 300 from sliding relative to each other during rotation of the nut 200. By arranging the outer contour of the washer 300 to be a direct sided shape, the relative sliding of the washer 300 can be limited by operating the wrench that rotates the nut 200 to ensure that the washer 300 and the nut 200 maintain a common rotational movement until the nut 200 and the bolt 100 are tightened. In order to facilitate the machining of the washer 300, the outer contour of the washer 300 may be machined into a regular hexagon having the same outer contour as the nut 200.

In the present application, the first pressing surface 230 and the second pressing surface 320 are disposed in various ways, including but not limited to the following two embodiments.

The first embodiment is as follows: as shown in fig. 1 to 4, opposite end surfaces of the nut 200 and the washer 300 are each disposed obliquely to form a first pressing surface 230 and a second pressing surface 320, respectively.

In this embodiment, the first extrusion surface 230 and the second extrusion surface 320 may be formed in various ways, including but not limited to the following two.

The first forming method comprises the following steps: the starting and ending points of the first pressing surface 230 and the second pressing surface 320 are located at any one pair of opposite sides of the nut 200 and the washer 300.

And a second molding mode: the starting and ending points of the first pressing surface 230 and the second pressing surface 320 are located at the maximum radial dimension positions of the nut 200 and the washer 300.

It will be appreciated that for the first molding described above, a special fixture is required for clamping, since the fixing along the edges of the blanks of the nut 200 and the washer 300 is required during the machining. In the second molding method, since the nut 200 and the spacer 300 are fixed along the side edges of the blank during the processing, only a common jig is required. Therefore, in order to facilitate processing and reduce production cost, the second molding method is preferably adopted in the present embodiment, and thus wrench operation can be facilitated while synchronous maximum rotation torque can be applied to the nut 200 and the washer 300, so as to ensure that the circumferential rotation directions of the nut 200 and the washer 300 are consistent, and only axial feeding is performed with respect to the bolt 100, thereby realizing tightening of the nut 200 by the washer 300 and the bolt 100.

Example two: as shown in fig. 5 to 10, opposite end surfaces of the nut 200 and the washer 300 are provided with at least one projection 240 and a groove 330, respectively. When the nut 200 and the bolt 100 are fastened, the nut 200 can drive the gasket 300 to synchronously rotate until the nut 200 and the bolt are fastened through the engagement of the protrusion 240 and the groove 330; at this time, the first pressing surface 230 is disposed on the protrusion 240, and the second pressing surface 320 is disposed on the groove 330.

It can be understood that, during the process of jointly driving the nut 200 and the washer 300 to rotate, the engagement between the protrusions 240 and the grooves 330 can further ensure that the nut 200 and the washer 300 can maintain synchronous rotation in the circumferential direction, so as to improve the self-locking performance of the nut 200.

In this embodiment, the specific number of the protrusions 240 and the grooves 330 may be set according to actual needs, for example, as shown in fig. 5 to 10, the number of the protrusions 240 and the grooves 330 is two pairs, and the two protrusions 240 and the grooves 330 of each pair are symmetrically disposed on two sides of the end surfaces of the nut 200 and the washer 300.

In this embodiment, the first pressing surface 230 and the second pressing surface 320 are disposed at various positions, including but not limited to the following two.

Setting a first position: the first pressing surface 230 and the second pressing surface 320 are respectively disposed at the top end of the protrusion 240 and the bottom end of the groove 330.

Specifically, the end surface of the tip end of the protrusion 240 extending toward the groove 330 is inclined to obtain the desired first pressing surface 230. The bottom of the groove 330 is also inclined at the same angle to obtain the desired second pressing surface 320. The first pressing surface 230 and the second pressing surface 320 formed by each protrusion 240 and the groove 330 are parallel to each other, so as to ensure that the force components generated by each first pressing surface 230 and the corresponding second pressing surface 320 can be equivalently combined.

Setting a second position: as shown in fig. 5 to 10, the first pressing surface 230 and the second pressing surface 320 are respectively disposed on the sides of the protrusion 240 and the groove 330 in the circumferential direction.

Specifically, the center of the washer 300 is provided with a second through hole 310, and the center of the nut 200 is provided with a threaded hole 210. The protrusion 240 and the groove 330 are located at the side of the nut 200 and the washer 300, respectively. The first pressing surface 230 and the second pressing surface 320 formed by each protrusion 240 and the groove 330 are parallel to each other, so as to ensure that the force components generated by each first pressing surface 230 and the corresponding second pressing surface 320 can be equivalently combined.

In one embodiment of the present application, as shown in fig. 3, 4, 8, 10 and 11, a second through hole 310 is formed in the center of the gasket 300, the diameter of the second through hole 310 is D, and the major diameter of the thread of the bolt 100 is D; D-D is less than or equal to 0.4mm.

It will be appreciated that to avoid or reduce the loss of the threads of bolt 100 by washer 300 during synchronous rotation with nut 200, second through hole 310 in the center of washer 300 may be sized to have a larger diameter than the threads of bolt 100. If the diameter D of the second through hole 310 is too large, the nut 200 and the bolt 100 may be tightened together, and the offset distance between the washer 300 and the nut 200 may be too large, which may cause uneven stress on the first pressing surface 230 and the second pressing surface 320. Therefore, the size of the second through hole 310 in the center of the gasket 300 is not excessively large. Generally, the diameter of the second through hole 310 at the center of the spacer 300 should not exceed the major diameter of the screw 100 by 0.4mm.

In this embodiment, as shown in fig. 2 and 6, the nut 200 has a first through hole 220 at the center of one end near the spacer 300, the first through hole 220 and the second through hole 310 have the same size, and the first through hole 220 is axially aligned with the threaded hole 210 of the nut 200.

It can be understood that, when the internal thread of the nut 200 is processed, the integrity of the thread generally needs to be ensured, so the length of the threaded hole 210 of the nut 200 needs to be smaller than the length of the nut 200, that is, the threaded hole 210 and the first pressing surface 230 are arranged at an interval by arranging the first through hole 220, and in order to ensure that the lower end of the nut 200 can be smoothly matched with the bolt 100, the size of the first through hole 220 may be larger than the thread major diameter of the bolt 100. For convenience of processing, it is preferable that the size of the first through hole 220 is set to be the same as that of the second through hole 310.

In one embodiment of the present application, as shown in fig. 1, 4, 5 and 10, the ramp-shaped self-locking fastener further includes a spring pad 400, and the spring pad 400 may be sleeved on the bolt 100, so that when the nut 200 and the bolt 100 are fastened together, the spring pad 400 may elastically abut against an end of the gasket 300 away from the nut 200.

It can be understood that, by providing the spring washer 400, the axial pressing force when the nut 200 and the bolt 100 are tightened can be increased, so as to improve the friction force of the nut 200 along the circumferential direction, so as to further improve the self-locking performance of the nut 200.

The foregoing has described the general principles, essential features, and advantages of the application. It will be understood by those skilled in the art that the present application is not limited to the embodiments described above, which are merely illustrative of the principles of the application, but that various changes and modifications may be made without departing from the spirit and scope of the application, and these changes and modifications are intended to be within the scope of the application as claimed. The scope of protection claimed by this application is defined by the following claims and their equivalents.

Claims

1. A ramp-shaped self-locking fastener, comprising: bolts, nuts and washers; the gasket is suitable for being sleeved on the bolt and is positioned between the bolt and the nut; the opposite end surfaces of the gasket and the nut are suitable for being matched through a slope-shaped structure, so that the nut drives the gasket to rotate around the bolt together until the gasket is tightened, and the slope-shaped structure locks the nut by generating a resultant moment along the radial direction.

2. The tapered self-locking fastener of claim 1, wherein: the slope-shaped structure comprises a first extrusion surface and a second extrusion surface; the first extrusion surface and the second extrusion surface are both obliquely arranged and have the same inclination angle; the first extrusion surface and the second extrusion surface are respectively arranged on the opposite end surfaces of the nut and the gasket, so that when the nut and the bolt are fastened together, the first extrusion surface and the second extrusion surface self-lock the nut through component force in the radial direction.

3. The tapered self-locking fastener of claim 2, wherein: the included angle between the first extrusion surface and the radial plane and the included angle between the second extrusion surface and the radial plane are larger than the friction angle between the contact surfaces of the nut and the gasket.

4. The tapered self-locking fastener of claim 2, wherein: the nut and the opposite end face of the gasket are obliquely arranged to form the first extrusion face and the second extrusion face respectively.

5. The tapered self-locking fastener of claim 4, wherein: the outer contour of the gasket is in a regular hexagon shape, and the size of the outer contour of the gasket is the same as that of the outer contour of the nut; the starting point and the end point of the first pressing surface and the second pressing surface are both located at the positions of the maximum radial dimension of the nut and the gasket.

6. The tapered self-locking fastener of claim 2, wherein: the opposite end surfaces of the nut and the gasket are respectively provided with at least one lug and a groove; when the nut and the bolt are tightly combined, the nut is suitable for driving the gasket to synchronously rotate until the gasket is tightly combined through the clamping of the convex block and the groove; the first extrusion surface is arranged on the convex block, and the second extrusion surface is arranged on the groove.

7. The tapered self-locking fastener of claim 6, wherein: the first extrusion surface and the second extrusion surface are respectively arranged at the top end of the bump and the bottom end of the groove;

or the first extrusion surface and the second extrusion surface are respectively arranged on the side edges of the lug and the groove along the circumferential direction.

8. The tapered self-locking fastener as claimed in any one of claims 1 to 7, wherein: a second through hole is formed in the center of the gasket, the diameter of the second through hole is D, and the major diameter of the thread of the bolt is D; D-D is less than or equal to 0.4mm.

9. The tapered self-locking fastener of claim 8, wherein: the nut is close to the center of one end of the gasket and is provided with a first through hole, the first through hole is the same as the second through hole in size, and the axes of the first through hole and the threaded hole of the nut are aligned.

10. The tapered self-locking fastener of claim 1, wherein: the slope-shaped self-locking fastener further comprises a spring pad, wherein the spring pad is suitable for being sleeved on the bolt, so that when the nut and the bolt are fastened, the spring pad is suitable for being elastically abutted to one end, far away from the nut, of the gasket.