CN219013134U - Slope-shaped eccentric self-locking fastening assembly - Google Patents

Abstract

The application discloses a slope eccentric self-locking fastening component, which comprises a nut and a gasket; the nut and the gasket are matched through the slope structure, so that the nut and the gasket are driven to move eccentrically in the radial direction through the slope structure in the process of fastening the nut, the gasket and the bolt, and the gasket and the bolt are extruded in the radial direction to form self-locking moment. The beneficial effects of this application: the gasket is added between the nut and the bolt, and the gasket is matched with the nut through the slope structure, so that when the nut and the bolt are tightly combined, the radial moment of couple is generated by extruding the bolt through radial movement of the gasket, and self-locking is realized. Moreover, the slope-shaped eccentric self-locking fastening assembly can meet the self-locking requirements of nuts of all specifications in all occasions, does not damage threads, can realize multiple detachable connection of the threads, and is adjustable in locking moment and reliable in self-locking.

Description

Slope-shaped eccentric self-locking fastening assembly

Technical Field

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

Background

Nut self-locking has great demands in various industries. The existing nut self-locking methods comprise a thread breaking stop method, an axial friction moment of couple self-locking method, a radial friction moment of couple self-locking method and the like. All the methods are realized by structural design on the structure of the nut, which easily causes the manufacturing structure of the nut to be complex, thereby increasing the manufacturing cost; or the structure of the nut is destroyed and the nut cannot be reused.

Disclosure of Invention

One of the purposes of the present application is to provide a sloping eccentric self-locking fastening assembly that is simple to manufacture and can be reused.

In order to achieve at least one of the above objects, the technical scheme adopted in the application is as follows: a slope-shaped eccentric self-locking fastening component comprises a nut and a gasket; the nut and the gasket are matched through a slope structure, so that the nut and the gasket are in fastening with the bolt, the gasket is driven to move eccentrically in the radial direction through the slope structure, and then the gasket and the bolt are extruded in the radial direction to form self-locking moment.

Preferably, the ramp structure comprises a first pressing surface and a second pressing 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 tightly combined, the first extrusion surface and the second extrusion surface are matched through extrusion to generate force for driving the gasket to radially move.

Preferably, an included angle between the radial plane and the first extrusion surface and an included angle between the radial plane and the second extrusion surface are alpha; and 0 DEG < alpha < 90 deg.

Preferably, the nut comprises a connecting section and a first boss, and the connecting section is suitable for being in threaded connection with the bolt through a set threaded hole; the first boss is arranged on the lower end face of the connecting section, and the first extrusion surface is arranged on one side of the first boss.

Preferably, the spacer comprises a support section and a second boss; the second boss is arranged on the upper end face of the supporting section, and the second extrusion surface is arranged on one side of the second boss.

Preferably, the start point and the end point of the extension surfaces of the first pressing surface and the second pressing surface are located at the positions of the maximum radial dimension of the nut and the gasket.

Preferably, the center of the gasket is provided with a through hole, the diameter D of the through hole is larger than the diameter D of the bolt, and D-D is smaller than or equal to 0.4mm.

Preferably, the through hole is eccentrically disposed such that an axis of the through hole has an eccentricity e with a center line of the gasket; and e- [ (D-D)/2-Z-k ] > 0; wherein Z represents the thread play between the nut and the bolt, and k represents the machining error.

Preferably, when the nut and the bolt are locked, a gap H exists between the nut and the gasket, so that the self-locking moment is adjusted by adjusting the value of the gap H.

Preferably, the outer contour of the gasket and the outer contour of the nut are regular hexagons, and the outer contour size of the gasket is the same as the outer contour size of the nut.

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

(1) The gasket is added between the nut and the bolt, and the gasket is matched with the nut through the slope structure, so that when the nut and the bolt are tightly combined, the radial moment of couple is generated by extruding the bolt through radial movement of the gasket, and self-locking is realized.

(2) Moreover, the slope-shaped eccentric self-locking fastening assembly can meet the self-locking requirements of nuts of all specifications in all occasions, does not damage threads, can realize multiple detachable connection of the threads, and is adjustable in locking moment and reliable in self-locking.

Drawings

Fig. 1 is a schematic cross-sectional view of the present utility model.

Fig. 2 is a schematic cross-sectional view of a nut according to the present utility model.

FIG. 3 is a schematic cross-sectional view of a gasket of the present utility model.

Fig. 4 is a schematic top view of a gasket according to the present utility model.

Fig. 5 is a schematic view of the present utility model in a stressed state during locking.

Fig. 6 is a schematic diagram of the self-locking stress state along the axial direction when the utility model is locked.

In the figure: nut 100, connection section 110, first boss 120, first compression surface 130, spacer 200, support section 210, second boss 220, second compression surface 230, through hole 240, bolt 300.

Detailed Description

The present application will be further described with reference to the specific embodiments, and it should be noted that, on the premise of no conflict, new embodiments may be formed by any combination of the embodiments or technical features described below.

In the description of the present application, it should be noted that, for the azimuth terms such as terms "center", "lateral", "longitudinal", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc., the azimuth and positional relationships are based on the azimuth or positional relationships shown in the drawings, it is merely for convenience of describing the present application and simplifying the description, and it is not to be construed as limiting the specific protection scope of the present application that the device or element referred to must have a specific azimuth configuration and operation, as indicated or implied.

It should be 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 objects and not necessarily for describing a particular sequential or chronological order.

One of the preferred embodiments of the present application, as shown in fig. 1 to 6, is a ramp-type eccentric self-locking fastening assembly comprising a nut 100 and a washer 200; the nut 100 and the gasket 200 are matched through the slope structure, so that in the process of fastening the nut 100, the gasket 200 and the bolt 300, the nut 100 and the gasket 200 are driven to radially and eccentrically move through the slope structure, and the gasket 200 and the bolt 300 are radially extruded to form self-locking moment.

It will be appreciated that in the process of tightening the nut 100 and the bolt 300, the washer 200 is first inserted into the bolt 300, and then the nut 100 and the bolt 300 are screwed together. In the process of screwing the nut 100, the washer 200 and the nut 100 are aligned through the slope structure, and then the washer 200 and the nut 100 are driven to rotate together through a tool such as a wrench, so that the interference of the washer 200 on the single rotation of the nut 100 is avoided.

In this embodiment, as shown in fig. 2 to 5, the slope structure includes a first pressing surface 130 and a second pressing surface 230; the first pressing surface 130 and the second pressing surface 230 are both inclined and have the same inclination angle; the first pressing surface 130 and the second pressing surface 230 are respectively disposed on opposite end surfaces of the nut 100 and the washer 200, so that when the nut 100 and the bolt 300 are fastened together, the first pressing surface 130 and the second pressing surface 230 are matched by pressing to generate a force for driving the washer 200 to radially move.

It can be appreciated that during the screwing process of the nut 100 and the bolt 300, the washer 200 is first moved to attach to the second pressing surface 230 and the first pressing surface 130 of the nut 100, and then the washer 200 and the nut 100 are simultaneously clamped by a wrench, so as to ensure that the nut 100 and the washer 200 rotate synchronously until the nut 100 is tightly screwed by the washer 200 and the bolt 300.

At this time, the nut 100 and the washer 200 are subjected to stress analysis.

As shown in fig. 5, the pressing forces generated by the first pressing surface 130 and the second pressing surface 230 pressing against each other are largely reversed, and are perpendicular to the first pressing surface 130 and the second pressing surface 230. The first component force in the axial direction and the second component force in the radial direction can be obtained by decomposing the pressing force between the first pressing surface 130 and the second pressing surface 230.

Wherein the first component force can drive the nut 100 and the bolt 300 to axially tighten until the resultant force of the first component force and the supporting force N of the head of the bolt 300 on the gasket 200 _Shaft Balancing is performed. At this time, the liquid crystal display device,the axial clearance of the threads between the nut 100 and the bolt 300 is eliminated so that self-locking of the nut 100 can be achieved by increasing the friction of the contact surface generated by the threaded engagement of the nut 100 and the bolt 300.

The second component force can respectively drive the gasket 200 and the nut 100 to respectively move along the direction a and the direction B, which are opposite to each other, until the resultant force of the second component force and the bolt 300 respectively balance the supporting forces of the nut 100 and the gasket 200. At this time, the positive pressure of the spacer 200 against the bolt 300 is N _A The positive pressure of the nut 100 to the bolt 300 is N _B Positive pressure N _A And N _B Are equal in size and opposite in direction. Due to positive pressure N _A And N _B The positions are different in the axial direction of the bolt 300 so that the positive pressure N _A And N _B A moment for overturning the nut 100 and the washer 200 can be generated in the axial plane of the bolt 300 to further improve the self-locking effect of the nut 100.

As shown in fig. 6, when the bolt 300 generates a moment M that loosens the nut 100 due to vibration or the like during use _{Pine nut} So that the nut 100 generates a movement trend in the loosening direction, the positive pressure N _A And N _B The generated friction moment M _A And M _B Just can sum to M _{Pine nut} The reverse direction can further prevent the nut 100 from loosening so as to further improve the self-locking of the nut 100.

In this embodiment, as shown in fig. 2 and 3, the first pressing surface 130 and the second pressing surface 230 have an angle α with respect to a radial plane, and 0 ° < α < 90 °.

It will be appreciated that nut 100 is press-fitted with washer 200 and nut 100 via first press surface 130 and second press surface 230 when tightened with bolt 300. When the nut 100 has a tendency to come loose, the nut 100 has a tendency to rotate helically with respect to the washer 200 due to the inclined arrangement of the first and second pressing surfaces 130 and 230.

At this time, as can be seen from the above-mentioned force analysis process, the pad 200 has a supporting force N _Shaft Friction against the rotation of the nut 100 is generated. And the supporting force N _Shaft Value of (2) and positive pressureForce N _A And N _B The resultant force at the contact plane of the first pressing surface 130 and the second pressing surface 230 is equally reversed; i.e. supporting force N _Shaft The value of (2) is related to the angle alpha; the greater the included angle alpha, the positive pressure N _A And N _B The larger the value of (c), the smaller the other way around. Therefore, the self-locking torque of the nut 100 can be adjusted by changing the value of the included angle alpha according to the application of the fastener in different working environments. Typically, the included angle α has a value in the range of 0-90 °.

In this embodiment, the first pressing surface 130 and the second pressing surface 230 are formed in various manners, including but not limited to the following two manners.

And a first molding mode is as follows: the start and end points of the extension surfaces of the first and second pressing surfaces 130 and 230 are located at any pair of opposite sides of the nut 100 and the washer 200.

And a second molding mode: the start and end points of the extension surfaces of the first and second pressing surfaces 130 and 230 are located at the positions of the maximum radial dimensions of the nut 100 and the washer 200.

It will be appreciated that for the first form described above, a special clamp is required to clamp the nut 100 and washer 200, as it is required to be secured along the edges of the blank during the machining process. In the second molding method, the fixing is performed only along the side edges of the blank member of the nut 100 and the washer 200, and therefore, only a general jig is required. Therefore, in order to facilitate processing and reduce production cost, the second molding mode is preferably adopted in this embodiment, and thus, the wrench operation can be facilitated, and simultaneously, synchronous maximum rotation torque can be applied to the nut 100 and the washer 200, so as to ensure that the circumferential rotation directions of the nut 100 and the washer 200 are consistent, and only axial feeding is performed with respect to the bolt 300, thereby realizing tightening of the nut 100 through the washer 200 and the bolt 300.

In this embodiment, as shown in fig. 2 and 5, the nut 100 includes a connection section 110 and a first boss 120, and the connection section 110 is adapted to be screwed with the bolt 300 through a set screw hole; the first boss 120 is disposed on a lower end surface of the connection section 110, and the first pressing surface 130 is disposed on one side of the first boss 120.

Specifically, as shown in fig. 2, the first boss 120 is located at a lower end surface of the connection section 110, that is, the projection of the first boss 120 along the axial direction can only cover a portion of the end surface of the connection section 110, so that when the first extrusion surface 130 is processed, it can be ensured that the extending height of the first boss 120 is reduced as much as possible under the condition that the included angle α of the first extrusion surface 130 meets the angle requirement, so as to avoid the overall length of the nut 100 being too long.

It can be appreciated that if the axial projection of the first boss 120 coincides with the end face of the connection section 110, the angle of the first pressing surface 130 is positively correlated with the height of the first boss 120 when the first pressing surface 130 is processed; i.e., the greater the value required for the included angle α, the greater the height of the first boss 120. With the design of the present embodiment, the angle of the first pressing surface 130 is irrelevant to the height and width of the first boss 120.

In this embodiment, as shown in fig. 3 to 5, the gasket 200 includes a support section 210 and a second boss 220; the second boss 220 is disposed on an upper end surface of the support section 210, and the second pressing surface 230 is disposed on one side of the second boss 220.

Specifically, as shown in fig. 3 and fig. 4, the second boss 220 is located at the upper end surface of the supporting section 210, that is, the projection of the second boss 220 along the axial direction can only cover the portion of the end surface of the supporting section 210, so that when the second extrusion surface 230 is processed, it can be ensured that the extending height of the second boss 220 is reduced as much as possible under the condition that the included angle α of the second extrusion surface 230 meets the angle requirement, so as to avoid the excessive thickness of the gasket 200.

It can be appreciated that if the axial projection of the second boss 220 coincides with the end surface of the support section 210, the angle of the second pressing surface 230 is positively correlated with the height of the second boss 220 when the second pressing surface 230 is processed; i.e., the greater the value required for the included angle α, the greater the height of the second boss 220. With the design of the present embodiment, the angle of the second pressing surface 230 is irrelevant to the height and width of the second boss 220.

In this embodiment, the center of the spacer 200 is provided with a through hole 240, and the diameter D of the through hole 240 is larger than the diameter D of the bolt 300, and D-D is less than or equal to 0.4mm. And, the through hole 240 is eccentrically disposed such that an eccentricity e exists between the axis B of the through hole 240 and the center line a of the gasket 200; and e- [ (D-D)/2-Z-k ] > 0; where Z represents the thread play between the nut 100 and the bolt 300, and k represents the machining error.

It will be appreciated that the through hole 240 in the center of the spacer 200 may be sized larger than the larger diameter of the threads of the bolt 300 in order to avoid or reduce the loss of the threads of the bolt 300 during the synchronous rotation of the spacer 200 with the nut 100. If the diameter D of the through hole 240 is too large, the nut 100 and the bolt 300 are easily tightened, and then the gasket 200 and the bolt 300 cannot be pressed against each other, so that the stress on the first pressing surface 130 and the second pressing surface 230 is small, and the self-locking requirement cannot be met. Therefore, the size of the through hole 240 in the center of the gasket 200 should not be excessively large. Generally, the diameter of the through hole 240 in the center of the gasket 200 should not exceed the larger diameter of the screw thread of the bolt 300 by 0.4mm.

Meanwhile, in order to ensure that the gasket 200 and the bolt 300 can be pressed after the nut 100 and the bolt 300 are fastened, it is necessary to ensure that the eccentricity e of the through hole 240 of the gasket 200 can satisfy a certain interference margin between the gasket 200 and the bolt 300. That is, when the nut 100 and the bolt 300 are fastened together, the gasket 200 and the bolt 300 are in interference fit, but the interference is not too large, and the excessive interference easily causes the bolt 300 to deform greatly, so that the bolt 300 is damaged and cannot be reused. Generally, the spacing between the spacer 200 and the bolt 300 includes the spacing (D-D)/2 of the major diameters of the threads of the through hole 240 and the bolt 300, the thread play Z of the bolt 300, and the machining error k of the part; therefore, the eccentricity e needs to be larger than (D-D)/2+Z+k.

It should be appreciated that the magnitude of the self-locking torque of nut 100 and washer 200 to bolt 300 is dependent upon the amount of interference between washer 200 and bolt 300. The interference between the gasket 200 and the bolt 300 is only required to be adjusted in order to adapt to the self-locking moment required by different use environments.

Specifically, as shown in fig. 1 and 5, when the nut 100 is locked with the bolt 300, a gap H exists between the nut 100 and the washer 200, so that the self-locking torque can be adjusted by adjusting the value of the gap H.

It can be understood that when a larger self-locking torque is required, the wrench can be operated by a larger driving force to drive the nut 100 and the gasket 200 to be screwed together, so that the gap H between the nut 100 and the gasket 200 is reduced, and the distance of the gasket 200 moving to one side can be further increased; i.e. the radial eccentricity deltae between the axis B of the through hole 240 on the washer 200 and the axis C of the nut 100 increases. When a small self-locking moment is needed, the spanner can be operated by a small driving force to drive the nut 100 and the gasket 200 to be screwed, so that a large gap H is formed between the nut 100 and the gasket 200, and the distance of the gasket 200 moving to one side can be shortened; i.e. the radial eccentricity deltae between the washer 200 and the nut 100 decreases.

For ease of understanding, the description may be by way of parameters. The radial eccentricity Δe=Δh/tan α between the washer 200 and the nut 100 may be set to Δh as the amount of change in the gap H between the nut 100 and the washer 200. Wherein the smaller the value of H, the larger the value of ΔH. Further, the self-locking moment of the washer 200 and the nut 100 to the bolt 300 has a value inversely proportional to the gap H between the nut 100 and the washer 200. That is, when the value of the angle α is determined, the larger the value of H, the smaller the value of the radial eccentricity Δe between the gasket 200 and the nut 100, the smaller the value of the self-locking moment generated by the gasket 200 and the nut 300; otherwise, the larger the value moment of the self-locking couple is. It should be noted that [ (D-D)/2-Z-k ] < Δe.ltoreq.e.

In this embodiment, as shown in fig. 4 and 6, the outer profile shapes of the washer 200 and the nut 100 may be regular polygons with an even number of arbitrary sides, and the distance between one pair of opposite sides of the washer 200 is equal to the distance between any pair of sides of the nut 100. To ensure that the washer 200 and the nut 100 are engaged, the washer 200 and the nut 100 are conveniently rotated together by a wrench.

It will be appreciated that washer 200 is capable of co-movement with nut 100 in order to ensure that nut 100 is threaded along bolt 300. It is necessary to restrict the washer 200 by a tool to avoid relative sliding of the washer 200 during rotation of the nut 100. By also providing the outer profile of washer 200 in a positive-sided shape, relative sliding of washer 200 may be limited together by manipulating the wrench that rotates nut 100 to ensure that washer 200 and nut 100 maintain a common rotational motion until nut 100 and bolt 300 are tightened. In order to facilitate the processing of the gasket 200, it is preferable that the outer contour of the gasket 200 is processed into a regular hexagon having the same outer contour as the nut 100.

The foregoing has outlined the basic principles, main features and advantages of the present application. It will be appreciated by persons skilled in the art that the present application is not limited to the embodiments described above, and that the embodiments and descriptions described herein are merely illustrative of the principles of the present application, and that various changes and modifications may be made therein without departing from the spirit and scope of the application, which is defined by the appended claims. The scope of protection of the present application is defined by the appended claims and equivalents thereof.

Claims (10)

1. The utility model provides a slope eccentric auto-lock fastening group spare, includes nut and gasket, its characterized in that: the nut and the gasket are matched through a slope structure, so that the nut and the gasket are in fastening with the bolt, the gasket is driven to move eccentrically in the radial direction through the slope structure, and then the gasket and the bolt are extruded in the radial direction to form self-locking moment.

2. The tapered eccentric self-locking fastener assembly as in claim 1, wherein: the slope 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 tightly combined, the first extrusion surface and the second extrusion surface are matched through extrusion to generate force for driving the gasket to radially move.

3. The tapered eccentric self-locking fastener assembly as claimed in claim 2, wherein: the included angle between the radial plane and the first extrusion surface and the second extrusion surface is alpha; and 0 DEG < alpha < 90 deg.

4. The tapered eccentric self-locking fastener assembly as claimed in claim 2, wherein: the nut comprises a connecting section and a first boss, and the connecting section is suitable for being in threaded connection with the bolt through a set threaded hole; the first boss is arranged on the lower end face of the connecting section, and the first extrusion surface is arranged on one side of the first boss.

5. The tapered eccentric self-locking fastener assembly as claimed in claim 2, wherein: the gasket comprises a support section and a second boss; the second boss is arranged on the upper end face of the supporting section, and the second extrusion surface is arranged on one side of the second boss.

6. The tapered eccentric self-locking fastener assembly as claimed in claim 2, wherein: the start and end points of the extension surfaces of the first and second pressing surfaces are located at the positions of the maximum radial dimensions of the nut and the washer.

7. A ramp-shaped over-center self-locking fastening assembly according to any one of claims 1-6, wherein: the center of the gasket is provided with a through hole, the diameter D of the through hole is larger than the diameter D of the bolt, and D-D is less than or equal to 0.4mm.

8. The tapered eccentric self-locking fastener assembly as in claim 7, wherein: the through holes are eccentrically arranged, so that an eccentric distance e exists between the axis of each through hole and the central line of the corresponding gasket; and e- [ (D-D)/2-Z-k ] > 0; wherein Z represents the thread play between the nut and the bolt, and k represents the machining error.

9. The tapered eccentric self-locking fastener assembly as in claim 8, wherein: when the nut and the bolt are locked, a gap H exists between the nut and the gasket, so that the self-locking moment is adjusted by adjusting the value of the gap H.

10. The tapered eccentric self-locking fastener assembly as in claim 1, wherein: the outer contour of the gasket and the outer contour of the nut are regular hexagons, and the outer contour size of the gasket is the same as the outer contour size of the nut.

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