Anti-stuck quick-release fastening assembly

Abstract

This invention discloses an anti-jamming quick-release fastening assembly, relating to the field of mechanical connection technology. This assembly aims to solve the problems of difficult disassembly and easy jamming of existing heavy-duty fasteners. It includes a screw, a nut threaded onto the screw, and an anti-loosening unit disposed between the locked plane and the nut. The anti-loosening unit consists of a first washer and a second washer coaxially arranged. The mating surface of the first washer has alternating first bosses and first grooves; the mating surface of the second washer has correspondingly alternating second bosses and second grooves. The first bosses and second grooves are opposite each other, and the second bosses and first grooves are opposite each other. This invention utilizes the relative rotation of the first and second washers to achieve mutual misalignment or embedded alignment of the first and second bosses, thereby changing the axial thickness of the anti-loosening unit and achieving rapid release of preload.

Description

Technical Field

[0001] This invention relates to the field of fastener technology, and more specifically, to a quick-release fastening assembly for use under high vibration conditions to prevent jamming. Background Technology

[0002] Bolt connections are the most basic and widely used fastening method. To prevent bolts from loosening under severe vibration, impact, or alternating loads, the industry has developed a variety of anti-loosening technologies.

[0003] Among them, double-layer self-locking washers based on the wedge-locking principle (such as designs conforming to DIN 25201) are widely used due to their significant anti-loosening effect. The principle is that the wedge angle on the inner side of the two washers is greater than the thread helix angle of the bolt. When the bolt loosens and rotates, the wedge slope between the washers will be axially lifted, thereby increasing the preload and physically preventing loosening.

[0004] Traditional washers, with their large continuous contact area, are prone to "cold welding" or corrosion adhesion under long-term high pressure or corrosive environments. Due to the large contact area, disassembly often requires extremely high destructive torque, frequently resulting in bolt breakage or tool damage. Summary of the Invention

[0005] The present invention aims to provide a quick-release fastening component that prevents jamming. It achieves instantaneous release of preload through a double-layer washer thickness variation mechanism, and combines a unique anti-reverse structure and a split tooth surface design to solve the problems of difficult disassembly and easy jamming.

[0006] To achieve the above objectives, the present invention provides an anti-jamming quick-release fastening assembly, including a screw, a nut threaded onto the screw, and an anti-loosening unit disposed between the locked plane and the nut. The anti-loosening unit includes a first washer and a second washer coaxially arranged. The first washer has a first mating surface facing the second washer, and the first mating surface has a first boss and a first groove alternating with the first boss; the second washer has a second mating surface facing the first washer, and the second mating surface has a second boss and a second groove alternating with the second boss. The first boss and the second groove are positioned opposite each other, and the second boss and the first groove are positioned opposite each other. By misaligning or aligning the first and second bosses, the axial thickness of the anti-loosening unit is changed.

[0007] Furthermore, the first washer has a locked position and a released position relative to the second washer. In the locked position, the surface of the first boss abuts against the surface of the second boss, and the anti-loosening unit is in its maximum axial thickness state, thereby maintaining the fastening force. In the released position, the first washer rotates a first angle relative to the second washer in the loosening direction, causing the first boss to slide down and be received in the second groove, and the second boss to slide down and be received in the first groove. At this time, the anti-loosening unit switches to its minimum axial thickness state, thereby quickly releasing the axial contact force between the nut and the first washer.

[0008] To ensure that the first washer rotates with the nut during disassembly to trigger the quick-release mechanism, the first washer has a driving surface on the side facing away from the first mating surface. This driving surface is used to contact the bottom surface of the nut. The driving surface is provided with a check-back protrusion structure. This structure is configured such that when the nut rotates in the unthreading (loosening) direction, the check-back protrusion structure mechanically engages or exerts high friction with the bottom surface of the nut, thereby causing the first washer to rotate synchronously relative to the second washer.

[0009] Preferably, the anti-reverse protrusion structure consists of multiple arc-shaped protrusions arrayed along the circumferential direction. Each arc-shaped protrusion includes a guide surface and an anti-reverse surface. The slope of the guide surface is smaller than that of the anti-reverse surface, allowing the nut to easily slide over the guide surface in the tightening direction, while being blocked by the anti-reverse surface in the unwinding direction. In a specific geometric design, the arc-shaped protrusion has an asymmetrical wavy shape in its axial cross-section. The angle between the tangent at the highest point of the arc-shaped protrusion and the bottom plane of the first washer is defined as the tangent angle. The tangent angle on the anti-reverse surface side is larger than that on the guide surface side, thereby creating a unidirectional driving effect.

[0010] For anti-jamming design, the second boss is not a continuous single unit, but rather composed of multiple independent and spaced-apart sub-tooth blocks. The combined projected profile of the multiple sub-tooth blocks matches the projected profile of the first boss; furthermore, stress relief grooves (or chip removal grooves / oil storage gaps) are provided between adjacent sub-tooth blocks. These stress relief grooves reduce the contact area between the second boss and the first boss, preventing large-area adhesion, and can accommodate wear debris or lubricating media, thus significantly reducing the risk of jamming.

[0011] Furthermore, to optimize smooth operation, the arc length and width of the first groove along the circumferential direction are greater than the arc length and width of the second boss along the circumferential direction. When the second boss is fully accommodated within the first groove, a play gap is formed between the sidewall of the second boss and the groove wall of the first groove. Additionally, the bottom surface of the first groove is a flat surface, and the plane containing this flat surface is perpendicular to the central axis of the screw. When the assembly is in the released position, the bottom surface of the second boss abuts against the flat surface, maintaining stable axial contact between the first and second washers.

[0012] The anti-jamming quick-release fastening assembly provided by this invention has the following beneficial effects: By utilizing the interlocking fit of the first and second washers, the axial thickness of the component can be significantly reduced after a slight rotation, instantly releasing the preload without having to overcome thread resistance throughout the process, unlike traditional nuts.

[0013] By improving the continuous boss into a split sub-tooth block design and setting stress relief grooves, the contact area under high pressure is effectively reduced, preventing cold welding jamming, while providing space to accommodate wear debris and lubricating grease.

[0014] The asymmetrical arc-shaped protrusion at the top (anti-reverse structure) cleverly utilizes the difference in tangent angles to achieve the function of "no interference when tightening and strong driving force when disassembling", ensuring the reliable triggering of the quick-release mechanism.

[0015] The sliding clearance design, with the groove width greater than the boss width, allows the component to smoothly enter the release state even under harsh working conditions, avoiding the inability to unlock due to mud or tolerances. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the overall structure of the anti-jamming quick-release fastening component of the present invention in the locked state.

[0017] Figure 2 This is an exploded structural diagram of the anti-loosening unit of the present invention.

[0018] Figure 3 This is a schematic diagram of the mating surface of the second washer.

[0019] Figure 4 This is a schematic diagram of the mating surface of the first washer.

[0020] Figure 5 This is a structural diagram of the component of the present invention in the released position, showing the state in which the two washers are interlocked.

[0021] Figure 6 This is a three-dimensional schematic diagram of the first washer drive surface, showing the anti-reverse protrusion structure used for unidirectional drive.

[0022] Figure 7 This is an enlarged schematic diagram of the axial cross-section of the anti-reverse protrusion structure, showing the difference in tangent angle between the guide surface and the anti-reverse surface. Detailed Implementation

[0023] This invention provides an anti-jamming quick-release fastening assembly 100, preferably used in the connection of equipment in heavy machinery, rail transportation, or environments subject to long-term vibration, dust, and high loads. See also Figures 1 to 5 The assembly generally includes a screw 110, a nut 120, and an anti-loosening unit 130 disposed between the nut 120 and the locked surface (such as an equipment support or mounting base 200). The nut 120 is conventionally threaded onto the screw 110 and is used to apply a preload to the locked workpiece; the anti-loosening unit 130 is coaxially sleeved on the outer periphery of the screw 110 and located between the bottom surface of the nut 120 and the locked surface, to ensure reliable fastening while enabling rapid release and preventing jamming.

[0024] like Figure 2 As shown, in this embodiment, the anti-loosening unit 130 includes a first washer 131 and a second washer 132 coaxially arranged. The first washer 131 is located on top, adjacent to the bottom surface of the nut 120; the second washer 132 is located on the bottom, adjacent to the locking surface. The first washer 131 has a first mating surface 133 facing the second washer 132, and the second washer 132 has a second mating surface 134 facing the first washer 131. The two are directly opposite each other in the assembled state.

[0025] See Figure 3 and Figure 4 A plurality of first protrusions 135 are provided on the first mating surface 133 along the circumferential direction, and a first groove 136 is formed between adjacent first protrusions 135; a plurality of second protrusions 137 are provided on the second mating surface 134 along the circumferential direction, and a second groove 138 is formed between adjacent second protrusions 137. The first protrusions 135 and the second grooves 138 are arranged opposite each other in the circumferential position, that is, when the first washer 131 is rotated relative to the second washer 132 to a certain predetermined angle (for example, in this application, the sector occupied by the first protrusion 135 and the groove is 60°, that is, the rotation angle is 60°), the first protrusion 135 can be aligned and slide into the second groove 138; similarly, the second protrusions 137 and the first grooves 136 are arranged opposite each other in the circumferential position, and can be accommodated in the first grooves 136 at the corresponding positions. By controlling the relative rotation between the first washer 131 and the second washer 132, the first boss 135 and the second boss 137 are positioned in an axial "butt-together" superimposed position (e.g., ...). Figure 1 (as shown) or "mutually nested" (as shown) Figure 5The different states (as shown) change the overall axial thickness of the anti-loosening unit 130, thereby achieving the switching between fastening and quick release.

[0026] In a preferred embodiment, the first washer 131 has two stable operating states relative to the second washer 132: a locked position and a released position. See also Figure 1 and Figure 4 When the nut 120 rotates in the tightening direction and applies a preload torque, the first washer 131 is pressed against the second washer 132 and is in a locked position. In this locked position, the surface of the first boss 135 abuts against the surface of the second boss 137, and the two overlap axially to form a "convex-to-convex" support state, thereby placing the anti-loosening unit 130 at its maximum axial thickness. At this time, the axial thickness of the assembly is approximately equal to the sum of the base thickness of the first washer 131, the base thickness of the second washer 132, and the effective overlap height of the first boss 135 and the second boss 137. The screw 110 is stretched to generate a preload force, and the nut 120 firmly presses the locked workpiece.

[0027] When disassembly is required, the operator rotates the nut 120 in the direction of thread removal. Driven by a specific structural fit, the first washer 131 rotates relative to the second washer 132 by a first angle in the loosening direction. See also... Figure 5 When the relative rotation angle reaches the predetermined first angle, the first boss 135 disengages from the top surface support of the second boss 137 and slides down into the second groove 138 under the action of reduced axial load and gravity or elastic force; at the same time, the second boss 137 also aligns with the first groove 136 and slides down into the first groove 136. At this time, both sets of bosses fall into the corresponding grooves, so that the first washer 131 and the second washer 132 are in an axially staggered nested state, and the overall axial thickness of the anti-loosening unit 130 instantly switches to the minimum axial thickness state. Since the support height drops sharply from the "superimposed height of the bosses" to "the height basically determined only by the thickness of the washer base", the original axial resistance between the bottom surface of the nut 120 and the first washer 131 is quickly released or even close to zero. The nut 120 then enters a "free-spinning" state with basically no preload. The operator can quickly unscrew the nut 120 without continuously overcoming high friction, thereby achieving a significant quick-release and anti-jamming effect.

[0028] To reliably trigger the aforementioned relative rotation during disassembly and ensure the repeatability of the quick-release action, this embodiment features a structural design for the side of the first washer 131 facing away from the first mating surface 133. See [link to previous section]. Figure 5 and Figure 6The side of the first washer 131 facing away from the first mating surface 133 is designated as the driving surface 139. This driving surface 139 faces the bottom surface of the nut 120 and is used for direct contact with the bottom surface of the nut 120. A check-back protrusion 140 is provided on the driving surface 139. When the nut 120 rotates in the unwinding direction, the check-back protrusion 140 and the bottom surface of the nut 120 (or the patterns or teeth on the bottom surface of the nut 120) generate mechanical engagement or high friction, thereby transmitting the torque of the nut 120 to the first washer 131. This causes the first washer 131 to rotate synchronously relative to the second washer 132, automatically transitioning the anti-loosening unit 130 from the locked position to the released position. This driving engagement ensures that under high load and high friction conditions, the operator only needs to apply a normal unwinding torque to trigger the relative rotation of the internal washers.

[0029] In a further preferred embodiment, the anti-reverse protrusion structure 140 on the drive surface 139 is composed of a plurality of arc-shaped protrusions 141 arranged in an array along the circumferential direction. See also Figure 5 Each arc-shaped protrusion 141 has a wave-like profile in its axial cross-section and includes two surfaces with distinctly different geometric features: a guide surface 142 and a check surface 143. The guide surface 142 is located on one side of the arc-shaped protrusion 141, with a gentle slope and a smooth transition. The check surface 143 is located on the other side of the arc-shaped protrusion 141, with a significantly greater slope than the guide surface 142, and can even be designed as an approximately upright or steep surface with a slight undercut. Through this asymmetrical slope design, when the nut 120 rotates in the tightening direction, the bottom surface of the nut 120 first contacts the guide surface 142. Under the action of axial clamping force, it can easily climb and slide over the guide surface 142, generating only limited frictional resistance. This prevents the first washer 131 from being forcibly driven to rotate, ensuring a smooth tightening process. When the nut 120 rotates in the direction of thread removal, the bottom surface of the nut 120 will slide to the highest point of the arc-shaped protrusion 141 and quickly contact the steep anti-reverse curved surface 143. Due to the large slope of the anti-reverse curved surface 143, the bottom surface of the nut 120 can hardly continue to pass over it. Significant mechanical interference or high frictional engagement is formed between the two, forcing the first washer 131 to rotate synchronously with the nut 120, thereby achieving unidirectional drive.

[0030] To further define the unidirectional driving effect of the arc-shaped protrusion 141 from a geometric perspective, this embodiment provides a parametric description of the cross-sectional shape and tangent angle of the arc-shaped protrusion 141. See [link to documentation]. Figure 7When viewed in cross-section along the axis of screw 110, the arc-shaped protrusion 141 exhibits an asymmetrical wavy profile in the axial section. It is not a symmetrical sine wave, but rather composed of curve segments with different radii of curvature. At the same height, a tangent is drawn to the guide surface 142 and the anti-reverse surface. This tangent forms an angle with the bottom plane of the first washer 131, called the tangent angle 144. On the anti-reverse surface 143 side of the arc-shaped protrusion 141, the tangent angle 144 is larger, and can be designed within the range of approximately 45° to 90°, resulting in a steeper or even nearly vertical edge. On the guide surface 142 side, the tangent angle 144' is smaller, and can be designed within the range of approximately 10° to 30°, resulting in a gentler slope. By making the tangent angle 144 on the anti-reverse surface 143 side significantly larger than the tangent angle 144 on the guide surface 142 side, the nut 120 is geometrically guaranteed to have good "slope crossing" in the tightening direction, while forming a ratchet-like anti-reverse barrier in the unwinding direction, thereby improving the reliability and efficiency of unidirectional drive.

[0031] In another embodiment, to adapt to harsh working conditions such as coal mines, silt, and metal dust environments where dust is high and corrosion is easily caused, the present invention improves the structure of the second boss 137 on the second washer 132. See also Figure 1 and Figure 3 In the basic embodiment, the second boss 137 can be designed as a continuous fan-shaped block along the circumferential direction, whose projected contour matches the first boss 135 to provide sufficient bearing area in the locking position. However, in this embodiment, the second boss 137 is not a single continuous block, but rather composed of multiple independent bosses. Specifically, the position that originally corresponded to a complete fan-shaped second boss 137 is divided into several independent boss units 145 spaced apart along the circumferential direction. The overall projection surface of the multiple independent boss units 145 in the axial direction of the second washer 132 coincides with or substantially coincides with the projection surface of the corresponding first boss 135 on the first washer 131. This ensures that in the locking position, the bottom surface of the first boss 135 can still effectively sit on the top surface of this group of combined bosses, with an overall support range comparable to the original continuous bosses, thereby guaranteeing reliable transmission of preload and axial bearing capacity.

[0032] Because the second boss 137 is segmented, gaps are naturally formed or pre-machined between each independent boss unit 145. These gaps constitute stress relief grooves 146, chip removal grooves, or oil storage gaps. The stress relief grooves 146 significantly reduce the contact area between the first boss 135 and the second boss 137, weakening the cold welding effect that may form on the metal surface under high pressure. This makes it easier to shear off microscopic adhesion points at the start of the release action, thereby reducing the initial disassembly torque and effectively preventing deadlock between the nut 120 and the washer. Furthermore, metal shavings generated during long-term vibration or repeated disassembly and assembly, as well as external sand and dust, can be scraped into and contained in these gaps, preventing hard particles from getting stuck on the main contact surface and causing severe abrasive wear or jamming. Simultaneously, the gap area can be pre-filled with grease, forming a local oil reservoir that continuously lubricates the mating surfaces during repeated rotation, further improving the smoothness of quick-disassembly operations.

[0033] To further improve the fault tolerance and anti-jamming capability when the boss falls into the groove, this embodiment optimizes the dimensional fit between the first groove 136 and the second boss 137 in the circumferential direction. See Figure 4 The first groove 136 is defined as having a first arc length width of 149 along its circumferential direction, and the second boss 137 is defined as having a second arc length width of 150 along its circumferential direction. In this embodiment, the first arc length width 149 is greater than the second arc length width 150, for example, it can be designed to be 1.2 to 1.5 times the second arc length width 150, i.e., a so-called "wide groove, narrow tooth" mating relationship. When the component moves from the locked position to the released position, that is, when the second boss 137 is fully aligned and slides into the first groove 136, since the groove width is greater than the boss width, the sidewall of the second boss 137 will not simultaneously abut against the two sides of the groove wall of the first groove 136, but a significant play gap 151 is formed between the boss sidewall and the groove wall. This play gap 151 significantly improves the tolerance of quick alignment, so that the operator does not need to precisely control the angle or rely on extremely fine machining precision, and the first boss 135 and the second boss 137 can fall smoothly into the corresponding groove, greatly improving the success rate of quick release. Meanwhile, the movement clearance 151 avoids an "overly tight fit" between the side wall of the boss and the groove wall. Even if there is thermal expansion or the entry of mud and sand particles, the boss can still fall smoothly under the action of gravity or load, avoiding "hanging and jamming" caused by side wall friction or foreign object blockage, and providing an escape channel for foreign objects.

[0034] Based on the aforementioned wide-groove, narrow-tooth fit, this embodiment further defines the bottom geometry of the first groove 136 to ensure the thickness stability and state reliability of the component in the release position. See also Figure 4The bottom surface of the first groove 136 is machined into a flat bottom surface 152. The geometric plane containing this flat bottom surface 152 is perpendicular to the central axis of the screw 110, that is, parallel to the overall reference plane of the washer, and has no slope along the axial direction. When the assembly is in the released position, the second boss 137 falls completely into the first groove 136, and its bottom surface forms a face-to-face contact with the flat bottom surface 152 of the first groove 136, thereby establishing a clear axial limit between the first washer 131 and the second washer 132 through planar support. This flat bottom structure gives the anti-loosening unit 130 a defined minimum axial thickness in the released position, and prevents thickness fluctuations due to vibration or external force; at the same time, since the bottom surface of the groove does not have a slope component, no horizontal component force is generated in the released state that causes the washer to climb circumferentially, thereby preventing the assembly from accidentally sliding back from the released state to the locked state under vibration, ensuring that the nut 120 can be stably maintained in a loose state with low load and easy unscrewing after quick release. If a small residual load remains at the release position, a flat surface contact can evenly distribute the residual load, avoiding localized stress concentration and indentation caused by point contact, and extending the life of the part.

[0035] In summary, this embodiment of the invention introduces an anti-loosening unit 130 composed of a first washer 131 and a second washer 132 between the screw 110 and the nut 120, and sets a relatively misaligned boss and groove structure between the two washers. This enables a rapid switch from maximum axial thickness to minimum axial thickness within a small turning angle, thereby quickly releasing the axial resistance between the nut 120 and the washer in the initial stage of disassembly and significantly reducing the disassembly torque. Simultaneously, the asymmetrical arc-shaped protrusion 141 anti-reverse protrusion structure 140 on the driving surface 139 of the first washer 131 ensures that the nut 120 automatically drives the first washer 131 to rotate in the unthreading direction without interference in the tightening direction. The design of the split second boss 137 and its stress relief groove 146 on the second washer 132 reduces the risk of cold welding and jamming and improves chip removal and lubrication capabilities. The wide groove, narrow teeth, and flat bottom geometry of the first groove 136 ensures smooth entry and stable support of the boss. These embodiments can be combined or selected independently.

Claims

1. An anti-stuck quick release fastening assembly, characterized by, Including is Screw; Nut, threaded connection to the screw rod; And an anti-loosening unit disposed between the locking plane and the nut, the anti-loosening unit comprising a first washer and a second washer coaxially disposed; The first washer has a first mating surface facing the second washer, and the first mating surface is provided with a first boss and a first groove disposed alternately with the first boss; The second washer has a second mating surface facing the first washer, and the second mating surface is provided with a second boss and a second groove disposed alternately with the second boss; The first boss and the second groove are positioned opposite each other, and the second boss and the first groove are positioned opposite each other. By misaligning or aligning the first boss and the second boss, the axial thickness of the anti-loosening unit is changed.

2. The anti-jamming quick-release fastening assembly according to claim 1, characterized in that: The first washer has a locked position and a released position relative to the second washer; In the locked position, the surface of the first boss abuts against the surface of the second boss, and the anti-loosening unit is in the maximum axial thickness state; In the released position, the first washer rotates by a first angle relative to the second washer in the loosening direction, causing the first boss to slide into the second groove and the second boss to slide into the first groove. The anti-loosening unit switches to the minimum axial thickness state to release the axial resistance between the nut and the first washer.

3. The anti-jamming quick-release fastening assembly according to claim 1, characterized in that: The first washer has a driving surface on the side facing away from the first mating surface, and the driving surface is used to contact the bottom surface of the nut; The drive surface is provided with a backstop protrusion structure. The backstop protrusion structure is configured such that when the nut rotates in the unthreading direction, the backstop protrusion structure and the bottom surface of the nut generate mechanical engagement or high friction, thereby driving the first washer to rotate synchronously relative to the second washer.

4. The anti-jamming quick-release fastening assembly according to claim 3, characterized in that: The anti-reverse protrusion structure is composed of multiple arc-shaped protrusions arranged in an array along the circumferential direction; Each of the arcuate protrusions includes a guide surface and a counter-rotating surface; The slope of the guide surface is less than that of the anti-reverse surface, which makes it easy for the nut to slide over the guide surface in the tightening direction, while it is blocked by the anti-reverse surface in the unwinding direction.

5. The anti-jamming quick-release fastening assembly according to claim 4, characterized in that: The arc-shaped protrusion has an asymmetrical wavy shape in the axial section; The tangent angle on the anti-reverse curved surface side is greater than the tangent angle on the guide curved surface side.

6. The anti-jamming quick-release fastening assembly according to claim 2, characterized in that: The second boss includes multiple independent bosses, the overall projection surface of which coincides with the first boss, and stress relief grooves are provided between the multiple independent bosses.

7. The anti-stuck quick release fastening assembly of claim 2, wherein The second boss is composed of multiple independent and spaced sub-tooth blocks; the combined projection profile of the multiple sub-tooth blocks is adapted to the projection profile of the first boss; and stress relief grooves are provided between adjacent sub-tooth blocks.

8. The anti-stuck quick release fastening assembly according to claim 7, wherein The arc length and width of the first groove along the circumferential direction are greater than the arc length and width of the second boss along the circumferential direction; when the second boss is completely contained in the first groove, a floating gap is formed between the side wall of the second boss and the groove wall of the first groove.

9. The anti-stuck quick release fastening assembly of claim 7, wherein the anti-stuck quick release fastening assembly is The bottom surface of the first groove is a flat bottom surface, and the plane on which the flat bottom surface is located is perpendicular to the central axis of the screw. When the component is in the released position, the bottom surface of the second boss is attached to the flat bottom surface, so that the first washer and the second washer maintain stable axial contact.

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