Bolt assembly and robot

Abstract

The utility model provides a bolt assembly and a robot. The bolt assembly comprises a nut and a bolt, the bearing part is arranged at one end of the nut and protrudes out of the outer surface of the nut in the radial direction of the nut; the end face, away from the nut, of the bearing part is obliquely arranged in the direction away from the nut in the direction from the peripheral face of the nut to the axis of the nut. According to the bolt assembly, the centering performance of the nut can be guaranteed, in the fastening operation process, relative sliding between the nut and a piece to be connected is effectively reduced, the fastening degree of connection is improved, and the loosening risk is reduced. Compared with a nut with the same radial size, the taper angle of the bearing part can be set to be large on the premise that the positioning effect and the stress area of the to-be-connected piece are ensured. Therefore, the axial length of the conical surface can be reduced, the overall size of the bolt is reduced, and the situation that the conical surface is embedded into a to-be-connected piece and is difficult to disassemble can be avoided.

Description

Technical Field

[0001] This utility model relates to the field of mechanical component design technology, and more specifically, to a bolt assembly and a robot. Background Technology

[0002] In the industrial field, bolted connections are a widely used fastening method, playing a crucial role in pre-tightened bolted connections subjected to large axial and overturning loads. To reduce bolt stress concentration and improve bolt strength, a common method is to improve the bolt or nut structure. However, related technical solutions have certain drawbacks. While adding a conical surface to the root of the nut or stud can improve centering, distribute force evenly on the bolt or nut, and enhance strength under the same radial dimensions, a smaller conical angle is often used to ensure positioning and increase the force-bearing area with the connected parts. This results in a longer axial length for the conical surface, a larger overall bolt size, and the possibility of the conical surface becoming embedded in the connected parts, making disassembly difficult, especially when the connected parts are made of soft materials.

[0003] Therefore, how to design a bolt assembly that can effectively reduce stress concentration, improve strength, avoid the conical surface from embedding into the connected parts, facilitate disassembly, and fully utilize the role of the conical surface in enhancing the stiffness of the connected parts has become an urgent problem to be solved. Utility Model Content

[0004] The present invention aims to at least solve the problems of tapered bolt assemblies using a smaller cone angle to ensure positioning effect and increase the force-bearing area with the parts to be connected, resulting in a longer axial length of the cone surface, a larger overall bolt size, and the cone surface being easy to embed into the parts to be connected, making disassembly difficult.

[0005] Therefore, the first aspect of this utility model provides a bolt assembly.

[0006] The second aspect of this utility model provides a robot.

[0007] In view of this, the first aspect of the present invention provides a bolt assembly, comprising: a nut; a bearing portion disposed at one end of the nut and protruding from the outer surface of the nut in the radial direction; the bearing portion being inclined in a direction away from the nut from the end face away from the nut in the direction from the outer circumferential surface of the nut to the axial direction of the nut.

[0008] The bolt assembly provided by this utility model includes a nut and a support portion. The support portion is disposed at one end of the nut and protrudes outward from the outer surface of the nut in the radial direction. That is, the outer diameter of the support portion is larger than the outer diameter of the nut. Therefore, when fixed by the nut, the support portion can increase the force-bearing area of ​​the connected parts, disperse the pressure of the nut on the surface of the connected parts, and reduce the local stress on the connected parts, thereby significantly improving the stability and reliability of the connection. The support portion is inclined away from the end face of the nut, along the outer circumference of the nut to the nut's axis, in a direction away from the nut, thus forming a conical surface. This further increases the contact area between the nut and the connected parts, further disperses the pressure of the nut on the surface of the connected parts, and reduces the local stress on the connected parts. Furthermore, the conical surface ensures the centering of the nut, effectively reducing the relative slippage between the nut and the connected parts during tightening operations, improving the tightness of the connection, and reducing the risk of loosening.

[0009] Secondly, since the outer diameter of the bearing portion of this application is larger than the outer diameter of the nut, compared to nuts of the same radial dimension, this application does not need to set the cone angle of the bearing portion too small to achieve the same effect as a regular tapered nut. In other words, the cone angle of the bearing portion can be set larger while ensuring the positioning effect and the force-bearing area with the connected parts. This not only reduces the axial length of the cone surface and the overall size of the bolt, but also avoids the cone surface embedding into the connected parts, making disassembly difficult, especially when the material of the connected parts is relatively soft.

[0010] The bolt assembly provided by this utility model may also have the following additional technical features:

[0011] In some embodiments, the bolt assembly may optionally include a stud, a nut disposed on the stud, and a bearing portion located between the nut and the member to be connected for abutting against the member to be connected.

[0012] In these embodiments, the bolt assembly further includes a stud, on which a nut is disposed and can be screwed to secure the connected parts. A bearing portion is located between the nut and the connected parts, so that when the nut is used for fixing, the bearing portion abuts against the connected parts, thereby increasing the force-bearing area and improving the stability of the connection.

[0013] In some embodiments, optionally, a nut is fixedly disposed at one end of a stud, and a bearing portion is located between the other end of the stud and the nut for abutting against the part to be connected; or the nut is detachably disposed on the stud, and the bearing portion is used for abutting against the part to be connected.

[0014] In these embodiments, two different configurations are used to secure the components to be connected. First, a nut can be fixed to one end of a stud, while a bearing portion is positioned between the other end of the stud and the nut, forming a single bolt structure. This configuration makes the bolt structure more robust, increasing its root strength and providing a more stable connection when securing the components. The bolt's tightening action ensures a tight connection, effectively preventing loosening or displacement during use, thus guaranteeing the reliability and safety of the connection. Second, the nut can be detachably mounted on the stud, offering greater flexibility in practical use. Specifically, one end of the stud is firmly fixed to one of the components to be connected, the other end of the stud is passed through other components, and finally, the nut is tightened onto the stud until the components are securely fixed. This detachable design makes it easy to disassemble and reassemble the connection points when needed, which is especially suitable for equipment or structures that require frequent maintenance, repair or replacement of parts, greatly improving work efficiency and reducing maintenance costs.

[0015] In some embodiments, the bolt assembly may optionally include a washer assembly disposed on the stud and located between the load-bearing portion and the member to be connected.

[0016] In these embodiments, a gasket assembly can also be provided between the load-bearing part and the component to be connected. This gasket assembly acts as a buffer, absorbing and dispersing the impact and vibration energy generated during the fastening process, reducing damage to the component to be connected and the bolt assembly itself, and extending the service life of the entire connection structure. Simultaneously, the gasket assembly increases the contact area, further dispersing the pressure of the load-bearing part on the component to be connected, resulting in a more uniform pressure distribution and reducing the risk of deformation or damage to the component to be connected due to excessive localized pressure.

[0017] In some embodiments, the gasket assembly may optionally include a tapered gasket that is inclined away from the nut along the axial direction from the outer peripheral surface of the nut to the nut.

[0018] In these embodiments, the gasket assembly includes a tapered gasket. Along the outer circumferential surface of the nut to the axial direction of the nut, the tapered gasket is inclined away from the nut. That is, the direction of the tapered structure formed by the tapered gasket is the same as the direction of the tapered structure formed by the bearing portion. This allows the tapered gasket to better fit with the tapered bearing portion. Secondly, the tapered gasket increases the contact area with the component to be connected, resulting in a more uniform pressure distribution and significantly reducing the possibility of the component being subjected to excessive local pressure. This effectively reduces the risk of deformation or damage to the component due to pressure concentration.

[0019] In some embodiments, optionally, the angle at which the bearing portion is inclined away from the end face of the nut away from the nut in the direction from the outer peripheral surface of the nut to the axial direction of the nut is equal to the angle at which the tapered washer is inclined away from the nut.

[0020] In these embodiments, along the axial direction from the outer circumference of the nut to its axis, the angle at which the bearing portion faces away from the nut is tilted away from the nut is the same as the angle at which the tapered washer tilts away from the nut. This equal angle design achieves a perfect match between the bearing portion and the tapered washer, allowing them to form a continuous and uniform pressure distribution surface when working together. This greatly optimizes pressure transmission and dispersion, avoiding component damage or connection failure caused by excessive local pressure. Simultaneously, the equal tilt angles ensure that the bearing portion and the tapered washer function synchronously during bolt tightening, jointly enhancing the stability and reliability of the connection. It reduces stress concentration and deformation caused by angular mismatch between components, improving the overall durability of the bolt assembly.

[0021] In some embodiments, the nut may optionally include: a first nut, fixedly mounted on one end of the stud; and a second nut, detachably mounted on the stud, wherein the bearing portion provided on the first nut is opposite to the bearing portion provided on the second nut.

[0022] In these embodiments, a first nut is fixedly installed at one end of a stud, forming a bolt structure. A second nut is then detachably installed on the stud, allowing the bolt structure to pass through the parts to be connected during use. The second nut is then screwed onto the other end of the stud, thus securing the parts. This method facilitates installation and disassembly, improving assembly and maintenance efficiency. Furthermore, positioning the load-bearing portions of the two nuts opposite each other ensures more even stress distribution at the connection, effectively dispersing pressure, reducing stress concentration, lowering the risk of loosening, and improving the reliability and stability of the connection.

[0023] In some embodiments, the gasket assembly may optionally include: a first gasket disposed on a stud, located between a first nut and the member to be connected; and / or a second gasket disposed on a stud, located between a second nut and the member to be connected.

[0024] In these embodiments, a first washer may be provided between the first nut and the component to be connected, and / or a second washer may be provided between the second nut and the component to be connected. By providing the first washer and / or the second washer, the tightening pressure from the first nut and / or the second nut can be absorbed and dispersed, reducing the local stress on the component to be connected and lowering the risk of deformation and breakage.

[0025] In some embodiments, optionally, one of the gasket assembly and the carrier portion is provided with a first anti-slip structure, and the other of the gasket assembly and the carrier portion is provided with a second anti-slip structure, the second anti-slip structure being adapted to the first anti-slip structure.

[0026] In these embodiments, one of the gasket assembly and the carrier portion is provided with a first anti-slip structure, and the other of the gasket assembly and the carrier portion is provided with a second anti-slip structure. The second anti-slip structure is adapted to the first anti-slip structure, thereby preventing the gasket assembly and the carrier portion from sliding against each other through the cooperation of the first and second anti-slip structures, and ensuring the stability of the connection.

[0027] In some embodiments, optionally, one of the gasket assembly and the member to be connected is provided with a third anti-slip structure, and the other of the gasket assembly and the member to be connected is provided with a fourth anti-slip structure, wherein the third anti-slip structure is adapted to the fourth anti-slip structure.

[0028] In these embodiments, one of the gasket assembly and the component to be connected is provided with a third anti-slip structure, and the other of the gasket assembly and the component to be connected is provided with a fourth anti-slip structure. The third anti-slip structure and the fourth anti-slip structure are adapted to each other, thereby preventing mutual sliding between the gasket assembly and the component to be connected through the cooperation of the third anti-slip structure and the fourth anti-slip structure, and ensuring the stability of the connection.

[0029] In some embodiments, optionally, the length of the bearing portion protruding from the outer surface of the nut in the radial direction is greater than or equal to 2 mm and less than or equal to 6 mm.

[0030] In these embodiments, by limiting the length of the bearing portion protruding from the outer surface of the nut to between 2 mm and 6 mm, sufficient bearing area can be ensured while avoiding excessive increase in the overall size and weight of the nut. A shorter protrusion length may not provide sufficient load-bearing capacity and contact area, while an excessively long protrusion will increase material consumption and processing costs, and may also lead to a decrease in the structural strength of the nut.

[0031] In some embodiments, optionally, along the outer peripheral surface of the nut to the axial direction of the nut, the angle at which the end face of the bearing portion away from the nut is inclined in the direction away from the nut is greater than or equal to 2.5° and less than or equal to 10°.

[0032] In these embodiments, along the outer circumferential surface of the nut to the axial direction of the nut, the angle at which the end face of the bearing portion facing away from the nut is inclined in the direction away from the nut is greater than or equal to 2.5° and less than or equal to 10°. This ensures that the end face of the bearing portion facing away from the nut forms a conical surface with a large cone angle. Therefore, while ensuring the positioning effect and the force-bearing area with the component to be connected, it not only reduces the axial length of the conical surface and the overall size of the bolt, but also avoids the situation where the conical surface embeds into the component to be connected, making disassembly difficult. It is understood that when the angle at which the end face of the bearing portion facing away from the nut is inclined in the direction away from the nut is greater than or equal to 2.5° and less than or equal to 10°, the angle at which the end face of the bearing portion facing away from the nut forms a cone angle greater than or equal to 160° and less than or equal to 175°. Setting a larger angle can prevent the conical surface from embedding into the component to be connected.

[0033] The second aspect of this application proposes a robot comprising: a bolt assembly as described in any of the technical solutions of the first aspect.

[0034] The robot provided in this application includes the bolt assembly as described in any of the technical solutions of the first aspect. Since the robot provided in this application includes the bolt assembly as described in any of the technical solutions of the first aspect, it also possesses all the beneficial effects of the bolt assembly as described in any of the technical solutions of the first aspect, which will not be elaborated further here.

[0035] Additional aspects and advantages of this invention will become apparent in the description that follows, or may be learned by practice of this invention. Attached Figure Description

[0036] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0037] Figure 1 One of the structural schematic diagrams of a bolt assembly according to an embodiment of the present invention is shown;

[0038] Figure 2 A second schematic diagram of the bolt assembly according to an embodiment of the present invention is shown;

[0039] Figure 3 The third schematic diagram shows the structure of a bolt assembly according to an embodiment of the present invention;

[0040] Figure 4 The fourth schematic diagram shows the structure of a bolt assembly according to an embodiment of the present invention;

[0041] Figure 5 One of the structural schematic diagrams of a gasket assembly according to an embodiment of the present invention is shown;

[0042] Figure 6A second schematic diagram of the gasket assembly according to an embodiment of the present invention is shown;

[0043] Figure 7 It shows Figure 6 Sectional view at point AA;

[0044] Figure 8 This illustration shows one of the structural schematic diagrams of a bolt assembly according to an embodiment of the present invention in a specific application.

[0045] Figure 9 The second schematic diagram shows the structure of a bolt assembly according to an embodiment of the present invention in a specific application.

[0046] Figure 10 The third schematic diagram shows the structure of a bolt assembly according to an embodiment of the present invention in a specific application.

[0047] Figure 11 The fourth schematic diagram shows the structure of a bolt assembly according to an embodiment of the present invention in a specific application.

[0048] Figure 12 The fifth schematic diagram shows the structure of a bolt assembly according to an embodiment of the present invention in a specific application.

[0049] Figure 13 The sixth schematic diagram shows the structure of a bolt assembly according to an embodiment of the present invention in a specific application.

[0050] Figure 14 The seventh schematic diagram shows the structure of a bolt assembly according to an embodiment of the present invention in a specific application.

[0051] Figure 15 This is shown as the eighth schematic diagram of the structure of a bolt assembly according to an embodiment of the present invention in a specific application.

[0052] Figure 16 This diagram illustrates the force distribution on a bolt under tension.

[0053] Figure 17 One of the schematic diagrams of the stress area of ​​the components to be connected is shown;

[0054] Figure 18 The second schematic diagram shows the stress zone of the component to be connected.

[0055] in, Figures 1 to 15 The correspondence between the reference numerals and component names in the attached drawings is as follows:

[0056] 1 Bolt assembly, 10 Nut, 102 First nut, 104 Second nut, 11 Bearing part, 12 Stud, 13 Washer assembly, 132 Conical washer, 134 First washer, 136 Second washer, 14 Rounded corner, 2 Parts to be connected. Detailed Implementation

[0057] To better understand the above-mentioned objectives, features, and advantages of this utility model, the present utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0058] Many specific details are set forth in the following description in order to provide a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Therefore, the scope of protection of the present invention is not limited to the specific embodiments disclosed below.

[0059] The following reference Figures 1 to 15 This invention describes bolt assemblies and robots proposed according to some embodiments of the present invention.

[0060] According to an embodiment of the first aspect of the present invention, such as Figures 1 to 15 As shown, the first aspect of this utility model provides a bolt assembly 1, including a nut 10 and a support portion 11. The support portion 11 is disposed at one end of the nut 10 and along the radial direction of the nut 10 (e.g., ...). Figure 1 The part (in the direction indicated by R) protrudes from the outer surface of the nut 10. It extends along the outer circumference of the nut 10 to the axial direction of the nut 10 (e.g., along the direction indicated by R). Figure 2 (in the direction indicated by M), the end of the bearing part 11 facing away from the nut 10 is inclined in a direction away from the nut 10.

[0061] The bolt assembly 1 provided by this utility model includes a nut 10 and a support portion 11. The support portion 11 is disposed at one end of the nut 10 and protrudes outward from the outer surface of the nut 10 in the radial direction. That is, the outer diameter of the support portion 11 is larger than the outer diameter of the nut 10. Therefore, when fixed by the nut 10, the support portion 11 can increase the force-bearing area of ​​the connected part 2, disperse the pressure of the nut 10 on the surface of the connected part 2, and reduce the local stress on the connected part, thereby significantly improving the stability and reliability of the connection. The support portion 11 is inclined away from the end face of the nut 10 and in the direction away from the axis of the nut 10 from the outer peripheral surface of the nut 10, thus forming a conical surface. This further increases the contact area between the nut 10 and the connected part 2, further disperses the pressure of the nut 10 on the surface of the connected part 2, and reduces the local stress on the connected part 2. Furthermore, the conical surface design ensures the centering of the nut 10, effectively reducing the relative slippage between the nut 10 and the part 2 to be connected during the tightening operation, improving the tightness of the connection, and reducing the risk of loosening.

[0062] Secondly, since the outer diameter of the bearing portion 11 is larger than that of the nut 10, compared to a nut 10 with the same radial dimension, this application does not need to set the cone angle of the bearing portion 11 too small to achieve the same effect as a regular tapered nut 10. In other words, the cone angle of the bearing portion 11 can be set larger while ensuring the positioning effect and the force-bearing area with the part to be connected 2. This not only reduces the axial length of the cone surface and the overall size of the bolt, but also avoids the cone surface from embedding into the part to be connected 2, making disassembly difficult, especially when the material of the part to be connected 2 is relatively soft.

[0063] In some embodiments, the connector 2 to be connected may optionally be provided with a tapered hole adapted to the support portion 11.

[0064] In some embodiments, the bolt assembly 1 may optionally include a stud 12, a nut 10 disposed on the stud 12, and a bearing portion 11 located between the nut 10 and the member to be connected 2 for abutting against the member to be connected 2.

[0065] In these embodiments, the bolt assembly 1 further includes a stud 12, on which a nut 10 is disposed and can be screwed to fix the member 2 to be connected. A bearing portion 11 is located between the nut 10 and the member 2 to be connected, so that when fixed by the nut 10, the bearing portion 11 can abut against the member 2 to be connected, thereby increasing the force-bearing area and improving the stability of the connection.

[0066] In some embodiments, optionally, the nut 10 is fixedly disposed at one end of the stud 12, and the bearing portion 11 is located between the other end of the stud 12 and the nut 10 for abutting against the part 2 to be connected; or the nut 10 is detachably disposed on the stud 12, and the bearing portion 11 is used to abut against the part 2 to be connected.

[0067] In these embodiments, two different configurations are used to fix the components 2 to be connected. First, the nut 10 can be fixed to one end of the stud 12, while the bearing portion 11 is positioned between the other end of the stud 12 and the nut 10, thus forming an integral bolt structure. This fixing method makes the bolt structure more stable, increasing its root strength and providing a more stable connection when fixing the components 2. Through the tightening action of the bolt, the components 2 can be tightly connected together, effectively preventing loosening or displacement during use, thereby ensuring the reliability and safety of the connection. Second, the nut 10 can be detachably mounted on the stud 12, offering greater flexibility in practical use. Specifically, one end of the stud 12 is first firmly fixed to one of the components 2 to be connected, then the other end of the stud 12 is passed through the other components 2, and finally, the nut 10 is tightened on the stud 12 until the components 2 are securely fixed. This detachable design makes it easy to disassemble and reassemble the connection points when needed, which is especially suitable for equipment or structures that require frequent maintenance, repair or replacement of parts, greatly improving work efficiency and reducing maintenance costs.

[0068] In some embodiments, the nut 10 and the stud 12 are optionally integrated.

[0069] In some embodiments, the bolt assembly 1 may optionally include a washer assembly 13 disposed on the stud 12 and located between the support portion 11 and the member to be connected 2.

[0070] In these embodiments, a gasket assembly 13 can also be provided between the bearing portion 11 and the component 2 to be connected. By providing the gasket assembly 13, a buffering effect is achieved, which can absorb and disperse the impact force and vibration energy generated during the fastening process, reducing damage to the component 2 to be connected and the bolt assembly 1 itself, and extending the service life of the entire connection structure. At the same time, the gasket assembly 13 also increases the contact area, further dispersing the pressure of the bearing portion 11 on the component 2 to be connected, making the pressure distribution more uniform, and reducing the risk of deformation or damage to the component 2 to be connected due to excessive local pressure.

[0071] In some embodiments, the gasket assembly 13 may optionally include a tapered gasket 132, which is inclined away from the nut 10 along the axial direction from the outer peripheral surface of the nut 10 to the nut 10.

[0072] In these embodiments, the gasket assembly 13 includes a tapered gasket 132. Along the outer circumferential surface of the nut 10 to the axial direction of the nut 10, the tapered gasket 132 is inclined away from the nut 10. That is, the direction of the tapered structure formed by the tapered gasket 132 is the same as the direction of the tapered structure formed by the bearing portion 11, thus allowing the tapered gasket 132 to better fit with the tapered bearing portion 11. Secondly, the tapered gasket 132 can increase the contact area with the component 2 to be connected, resulting in a more uniform pressure distribution and significantly reducing the possibility of the component 2 being subjected to excessive local pressure. This effectively reduces the risk of deformation or damage to the component 2 due to pressure concentration.

[0073] In some embodiments, optionally, along the axial direction from the outer peripheral surface of the nut 10 to the axis of the nut 10, the end face of the bearing portion 11 facing away from the nut 10 is inclined at an angle away from the nut 10. Figure 2 (As indicated by α), is equal to the angle at which the conical washer 132 is tilted away from the nut 10.

[0074] In these embodiments, along the axial direction from the outer circumferential surface of the nut 10 to the axis of the nut 10, the angle at which the end face of the bearing portion 11 facing away from the nut 10 is tilted away from the nut 10 is set to be the same as the angle at which the conical washer 132 is tilted away from the nut 10. This equal angle design achieves a perfect match between the bearing portion 11 and the conical washer 132, enabling them to form a continuous and uniform pressure distribution surface when working together. This greatly optimizes the transmission and dispersion of pressure, avoiding component damage or connection failure caused by excessive local pressure. At the same time, the equal tilt angle ensures that the bearing portion 11 and the conical washer 132 can function synchronously during bolt tightening, jointly enhancing the stability and reliability of the connection. It reduces stress concentration and deformation caused by angular mismatch between components, improving the durability of the entire bolt assembly 1.

[0075] In some embodiments, the nut 10 may optionally include: a first nut 102, which is fixedly installed on one end of the stud 12; and a second nut 104, which is detachably installed on the stud 12, wherein the bearing portion 11 provided on the first nut 102 is opposite to the bearing portion 11 provided on the second nut 104.

[0076] In these embodiments, a first nut 102 is fixedly installed at one end of a stud 12, forming a bolt structure. A second nut 104 is then detachably installed on the stud 12, allowing the bolt structure to pass through the part to be connected 2 during use. The second nut 104 is then screwed onto the other end of the stud 12, thus securing the part to be connected 2. This method facilitates installation and disassembly, improving assembly and maintenance efficiency. Simultaneously, the opposing bearing portions 11 on the two nuts 10 allow for more even force distribution at the connection point, effectively dispersing pressure, reducing stress concentration, lowering the risk of loosening, and improving the reliability and stability of the connection.

[0077] In some embodiments, the gasket assembly 13 may optionally include: a first gasket 134 disposed on the stud 12 and located between the first nut 102 and the member to be connected 2; and / or a second gasket 136 disposed on the stud 12 and located between the second nut 104 and the member to be connected 2.

[0078] In these embodiments, a first washer 134 may be provided between the first nut 102 and the component 2 to be connected, and / or a second washer 136 may be provided between the second nut 104 and the component 2 to be connected. By providing the first washer 134 and / or the second washer 136, the tightening pressure from the first nut 102 and / or the second nut 104 can be absorbed and dispersed, reducing the local stress on the component 2 to be connected and lowering the risk of deformation and breakage.

[0079] In some embodiments, optionally, one of the pad assembly 13 and the support portion 11 is provided with a first anti-slip structure, and the other of the pad assembly 13 and the support portion 11 is provided with a second anti-slip structure, the second anti-slip structure being adapted to the first anti-slip structure.

[0080] In these embodiments, one of the gasket assembly 13 and the support portion 11 is provided with a first anti-slip structure, and the other of the gasket assembly 13 and the support portion 11 is provided with a second anti-slip structure. The second anti-slip structure is adapted to the first anti-slip structure, thereby preventing the gasket assembly 13 and the support portion 11 from sliding against each other through the cooperation of the first anti-slip structure and the second anti-slip structure, and ensuring the stability of the connection.

[0081] In some embodiments, optionally, one of the gasket assembly 13 and the carrier portion 11 is provided with a groove, and the other of the gasket assembly 13 and the carrier portion 11 is provided with a protrusion that is adapted to the groove.

[0082] In some embodiments, optionally, one of the gasket assembly 13 and the member to be connected 2 is provided with a third anti-slip structure, and the other of the gasket assembly 13 and the member to be connected 2 is provided with a fourth anti-slip structure, wherein the third anti-slip structure is adapted to the fourth anti-slip structure.

[0083] In these embodiments, one of the gasket assembly 13 and the component to be connected 2 is provided with a third anti-slip structure, and the other of the gasket assembly 13 and the component to be connected 2 is provided with a fourth anti-slip structure. The third anti-slip structure and the fourth anti-slip structure are adapted to each other, thereby preventing mutual sliding between the gasket assembly 13 and the component to be connected 2 through the cooperation of the third anti-slip structure and the fourth anti-slip structure, and ensuring the stability of the connection.

[0084] In some embodiments, optionally, the length by which the bearing portion 11 protrudes from the outer surface of the nut 10 in the radial direction of the nut 10 (e.g., ...) Figure 1 (The part indicated by H) is greater than or equal to 2 mm and less than or equal to 6 mm.

[0085] In these embodiments, by limiting the length of the bearing portion 11 protruding from the outer surface of the nut 10 to between 2 mm and 6 mm, it is possible to ensure sufficient bearing area while avoiding excessive increase in the overall size and weight of the nut 10. A shorter protrusion length may not provide sufficient load-bearing capacity and contact area, while an excessively long protrusion will increase material consumption and processing costs, and may also lead to a decrease in the structural strength of the nut 10.

[0086] In some embodiments, optionally, the length of the bearing portion 11 protruding from the outer surface of the nut 10 in the radial direction of the nut 10 is 2 mm.

[0087] In some embodiments, optionally, the length of the bearing portion 11 protruding from the outer surface of the nut 10 in the radial direction of the nut 10 is 3 mm.

[0088] In some embodiments, optionally, the length of the bearing portion 11 protruding from the outer surface of the nut 10 in the radial direction of the nut 10 is 4 mm.

[0089] In some embodiments, optionally, the length of the bearing portion 11 protruding from the outer surface of the nut 10 in the radial direction of the nut 10 is 5 mm.

[0090] In some embodiments, optionally, the length of the bearing portion 11 protruding from the outer surface of the nut 10 in the radial direction of the nut 10 is 6 mm.

[0091] In some embodiments, optionally, along the outer peripheral surface of the nut 10 to the axial direction of the nut 10, the angle at which the end face of the bearing portion 11 facing away from the nut 10 is inclined in a direction away from the nut 10 is greater than or equal to 2.5° and less than or equal to 10°.

[0092] In these embodiments, along the axial direction from the outer circumference of the nut 10 to its axis, the angle at which the end face of the bearing portion 11 facing away from the nut 10 is inclined in a direction away from the nut 10 is greater than or equal to 2.5° and less than or equal to 10°. This ensures that the end face of the bearing portion 11 facing away from the nut 10 forms a conical surface with a large cone angle. Therefore, while ensuring the positioning effect and the force-bearing area with the component 2 to be connected, it not only reduces the axial length of the conical surface and the overall size of the bolt, but also prevents the conical surface from embedding into the component 2 to be connected, thus avoiding difficulties in disassembly. It is understood that when the angle at which the end face of the bearing portion 11 facing away from the nut 10 is inclined in a direction away from the nut 10 is greater than or equal to 2.5° and less than or equal to 10°, the angle at which the end face of the bearing portion 11 facing away from the nut 10 forms a cone angle greater than or equal to 160° and less than or equal to 175°. Setting a larger angle can prevent the conical surface from embedding into the component 2 to be connected.

[0093] In some embodiments, optionally, the end face of the bearing portion 11 facing away from the nut 10 is inclined at an angle of 2.5° in the direction away from the nut 10 along the outer peripheral surface of the nut 10 to the axial direction of the nut 10.

[0094] In some embodiments, optionally, the end face of the bearing portion 11 facing away from the nut 10 is inclined at an angle of 4° in the direction away from the nut 10 along the outer peripheral surface of the nut 10 to the axis of the nut 10.

[0095] In some embodiments, optionally, the end face of the bearing portion 11 facing away from the nut 10 is inclined at an angle of 6° in the direction away from the nut 10 along the outer peripheral surface of the nut 10 to the axis of the nut 10.

[0096] In some embodiments, optionally, the end face of the bearing portion 11 facing away from the nut 10 is inclined at an angle of 8° in the direction away from the nut 10 along the outer peripheral surface of the nut 10 to the axis of the nut 10.

[0097] In some embodiments, optionally, the end face of the bearing portion 11 facing away from the nut 10 is inclined at an angle of 10° in the direction away from the nut 10 along the outer peripheral surface of the nut 10 to the axial direction of the nut 10.

[0098] Optionally, when the nut 10 is fixedly mounted on the stud 12, the connection between the nut 10 and the stud 12 is provided with a fillet 14 or a chamfer; and / or the connection between the support portion 11 and the nut 10 is provided with a fillet 14 or a chamfer; and / or the connection between the support portion 11 and the stud 12 is provided with a fillet 14 or a chamfer; and / or the transition surfaces of the support portion 11 are provided with a fillet 14 or a chamfer; and / or the transition surfaces of the gasket assembly 13 are provided with a fillet 14 or a chamfer.

[0099] In these embodiments, by providing fillet 14 or chamfer, stress concentration at the connection can be reduced, significantly improving the strength and durability of the connection structure.

[0100] In some embodiments, the nut 10 is optionally provided with an internal thread, and at least a portion of the stud 12 is provided with an external thread. The internal thread of the nut 10 and the external thread of the stud 12 can engage with each other.

[0101] In some embodiments, the nut 10 may be a hexagonal nut 10.

[0102] In some embodiments, the support portion 11 and the nut 10 are optionally integrated.

[0103] In some embodiments, the conical gasket 132 may optionally have grooves or ridges on the surface where it mates with the bolt and the component 2 to be connected, in order to prevent slipping and loosening.

[0104] In some embodiments, the outer edge of the tapered nut 10 and the tapered washer 132 are optionally provided with anti-loosening structures, such as anti-loosening tongues and pin holes, to achieve the purpose of preventing bolt loosening.

[0105] According to an embodiment of the first aspect of this utility model, a bolt assembly 1 is provided, which can withstand large axial or overturning loads. The bolt assembly 1 includes a tapered bolt (formed by fixing a tapered nut 10 and a stud 12 together), a tapered washer 132, and a tapered nut, all three having the same cone angle. The bolt hole of the component to be connected 2 is also tapered, with the same cone angle as the tapered washer 132. By engaging the tapered surface of the bolt, nut 10, or washer with the component to be connected 2, the stress-bearing area and stiffness of the component to be connected 2 can be increased while maintaining a smaller radial dimension. In use, the tapered surface of the tapered washer 132 is recessed into the tapered hole of the component to be connected 2, resulting in a smaller axial dimension for the entire bolted connection. The tapered fit provides good centering, improves bolt positioning accuracy, and reduces stress concentration in the bolt. Furthermore, the tapered structure of the stud 12 also increases its root strength and provides a smoother transition to the bolt head, further reducing stress concentration. Furthermore, the tapered washer 132 has a large cone angle, which can increase the bearing area of ​​the component 2 to be connected and prevent the tapered surface from embedding into the component 2 to be connected. When the external bending moment load causes the washer to sway in the tapered hole of the component 2 to be connected, the protruding outer edge (bearing part 11) of the bolt head and nut 10 can provide elastic buffering to reduce the impact on the bolt.

[0106] The bolt assembly 1 provided in this application has a reliable connection structure, is simple to process and manufacture, can be reused, has a wide range of applications, and has great market value.

[0107] In some embodiments, the nut 10, the bearing portion 11, and the stud 12 are optionally integrated into one piece. In this case, the nut 10 plus the bearing portion 11 constitutes the bolt head.

[0108] In some embodiments, the stud 12 and nut 10 may have a fillet 14 at the connection with the support portion 11 to reduce stress concentration at the connection.

[0109] In some embodiments, optionally, such as Figure 1 , Figure 2 , Figure 3 and Figure 4 As shown, the tapered section (bearing part 11) of the bolt head and nut 10 exceeds its radial dimension by 2mm to 6mm, which can increase the contact area between the bolt assembly 1 and the part 2 to be connected.

[0110] In some embodiments, optionally, such as Figure 5 , Figure 6 and Figure 7 The conical gasket 132 has the same cone angle on both sides, and the cone apex is in the same direction. Both the inner and outer edges of the gasket have rounded corners 14.

[0111] In some embodiments, the tapered bolt, tapered washer 132 and tapered nut 10 may optionally have a tapered angle of 160° to 175°. A larger tapered angle can increase the bearing area of ​​the component 2 to be connected and prevent the tapered surface from embedding into the component 2 to be connected.

[0112] When an external bending moment load causes the shim to wobble in the tapered hole of the part to be connected 2, the protruding outer edge (bearing part 11) of the bolt head and nut 10 can provide elastic cushioning to reduce the impact on the bolt.

[0113] In addition, the tapered structure also makes the root of the stud 12 stronger and the transition with the bolt head smoother, reducing stress concentration.

[0114] The specific installation and usage methods of the bolt assembly in this application are as follows:

[0115] For bolted connections where the materials to be connected are relatively soft or brittle, use, for example... Figure 8 and Figure 9 The connection is made as shown. First, pass the tapered bolt through the tapered washer and the part to be connected in sequence. Then, insert another tapered washer through the end of the bolt, with the cone of the tapered washer facing the part to be connected. Next, screw the tapered nut into the tapered bolt to a certain depth so that the tapered washer, tapered bolt, tapered nut and the tapered surface of the connected tapered hole fit together. Finally, tighten it to the desired state.

[0116] For bolt connections where the materials to be connected are relatively hard, use, for example... Figure 10 and Figure 11 The connection is made as shown. First, pass the tapered bolt through the parts to be connected, then screw the tapered nut into the bolt to a certain depth, so that the tapered bolt, tapered nut and tapered surface of the connected hole fit together, and finally tighten to the desired state.

[0117] For screw connections where the materials to be connected are relatively soft or brittle, use, for example... Figure 12 and Figure 13 The connection is performed as shown. First, pass the tapered bolt through the tapered washer and the parts to be connected in sequence. Then, insert the end of the bolt into the threaded hole of the base plate, and then screw it into the threaded hole to a certain depth so that the tapered washer, tapered bolt and the tapered surface of the connected tapered hole fit together. Finally, tighten it to the required state.

[0118] For screw connections where the materials to be connected are relatively hard, use, for example... Figure 14 and Figure 15 The connection is performed as shown. First, pass the tapered bolt through the parts to be connected. Then, insert the end of the bolt into the threaded hole of the base plate. Next, screw it into the threaded hole to a certain depth so that the tapered bolt and the tapered surface of the connected hole fit together. Finally, tighten it to the desired state.

[0119] in, Figure 13 and Figure 15 The dashed line in the diagram represents the center line.

[0120] The principle and function of the bolt assembly in this application are as follows:

[0121] Existing bolts often use a small taper angle to improve centering, resulting in a longer axial length of the taper surface, a larger overall bolt size, and the risk of the taper surface embedding into the workpiece to be connected. Furthermore, for the same radial dimension, a tapered surface has a larger contact area than a horizontal surface, but existing washers with tapered contact surfaces have a small taper angle, making them prone to embedding into the workpiece and difficult to disassemble. Washers with larger taper angles mostly only consider the centering effect of the taper, failing to utilize the function of the taper surface in improving the stiffness of the workpiece to be connected.

[0122] This application discloses a high-load-bearing bolted connection structure. By using a bolt or nut, a washer, and the conical surface of the connected component to engage, the structure can increase the stress-bearing area and stiffness of the connected component while maintaining a small radial dimension. In use, the conical surface of the washer is recessed into the conical hole of the connected component, resulting in a smaller axial dimension for the entire bolted connection. The conical fit provides good centering, improves bolt positioning accuracy, and reduces stress concentration in the bolt. The conical washer has a large cone angle, increasing the load-bearing area of ​​the connected component while preventing the conical surface from embedding into it. When external bending moment loads cause the washer to wobble in the conical hole of the connected component, the protruding outer edges of the bolt head and nut provide elastic cushioning, reducing the impact on the bolt.

[0123] The force-bearing principle of the bolt assembly in this application is described as follows:

[0124] 1. Calculation of the force on the preloaded bolts:

[0125] The force diagram of the preloaded bolt under axial force is as follows: Figure 16As shown in the figure. Where F0 is the bolt preload and F1 is the applied axial force.

[0126] The total bolt tension F2 can be expressed as follows:

[0127]

[0128] Among them, C b For the stiffness of the bolt, C m For the stiffness of the parts to be connected, This refers to relative stiffness.

[0129] As can be seen from the above formula, increasing the stiffness of the connecting parts is beneficial to enhancing the bolt's load-bearing capacity.

[0130] 2. Stiffness C of the components to be connected m The calculation method is as follows:

[0131] The stress-bearing area of ​​the components to be connected is equivalent to a combination of two cones and one cylinder, such as... Figure 17 As shown. The horizontal line area represents the stress area of ​​the component to be connected, d w Where d is the outer diameter of the contact area between the bolt and the workpiece to be connected, L is the total thickness of the workpiece to be connected, and d is the outer diameter of the contact area between the bolt and the workpiece to be connected. h Let θ be the inner diameter of the bolt hole, h be the cone angle, h be the cone height, and d be the outer diameter of the bolt. A This refers to the outer diameter of the stress-bearing area of ​​the component to be connected.

[0132] The calculation of the stiffness of the components to be connected is related to the contact pose of the bolt and the components to be connected. Figure 18 This paper compares the stress regions of the connected components in a tapered bolt connection and a conventional bolt connection at the same angle θ. The thick, short dashed line represents the stress region of the tapered bolt connection, while the thin, short dashed line represents the stress region of the conventional bolt connection.

[0133] from Figure 18 It is known that a tapered shape can greatly improve the stiffness of the parts to be connected, which helps to improve the load-bearing capacity of the bolts.

[0134] The second aspect of this application proposes a robot comprising: a bolt assembly 1 as described in any embodiment of the first aspect.

[0135] The robot provided in this application includes the bolt assembly 1 in any embodiment of the first aspect. Since the robot provided in this application includes the bolt assembly 1 in any embodiment of the first aspect, it also possesses all the beneficial effects of the bolt assembly 1 in any embodiment of the first aspect, which will not be elaborated further here.

[0136] In some embodiments, the robot may optionally include a component 2 to be connected, which has a through hole or a blind hole, and a tapered hole at the opening of the through hole or blind hole, which is adapted to the support portion 11 or the pad assembly 13.

[0137] In this utility model, the term "multiple" refers to two or more unless otherwise explicitly defined. The terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; "linking" can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0138] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0139] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A bolt assembly, characterized in that, include: Nut; A support portion is provided at one end of the nut and protrudes from the outer surface of the nut in the radial direction; Along the outer circumferential surface of the nut to the axial direction of the nut, the end face of the bearing portion opposite to the nut is inclined in a direction away from the nut.

2. The bolt assembly according to claim 1, characterized in that, Also includes: A stud, wherein the nut is disposed on the stud, and the bearing portion is located between the nut and the part to be connected, for abutting against the part to be connected.

3. The bolt assembly according to claim 2, characterized in that, The nut is fixedly disposed at one end of the stud, and the bearing portion is located between the other end of the stud and the nut, for abutting against the part to be connected; or The nut is detachably mounted on the stud, and the bearing portion is used to abut against the part to be connected.

4. The bolt assembly according to claim 2, characterized in that, Also includes: A gasket assembly is disposed on the stud and located between the bearing portion and the component to be connected.

5. The bolt assembly according to claim 4, characterized in that, The gasket assembly includes a tapered gasket that is inclined away from the nut along the outer circumferential surface of the nut to the axial direction of the nut.

6. The bolt assembly according to claim 5, characterized in that, Along the outer circumferential surface of the nut to the axial direction of the nut, the angle at which the end face of the bearing portion away from the nut is inclined in a direction away from the nut is equal to the angle at which the tapered washer is inclined in a direction away from the nut.

7. The bolt assembly according to claim 4, characterized in that, The nut includes: The first nut is fixedly installed at one end of the stud. The second nut is detachably installed on the stud, and the bearing portion provided on the first nut is opposite to the bearing portion provided on the second nut.

8. The bolt assembly according to claim 7, characterized in that, The gasket assembly includes: A first washer is disposed on the stud, located between the first nut and the component to be connected; and / or The second washer is disposed on the stud and located between the second nut and the part to be connected.

9. The bolt assembly according to claim 4, characterized in that, One of the gasket assembly and the support portion is provided with a first anti-slip structure, and the other of the gasket assembly and the support portion is provided with a second anti-slip structure, the second anti-slip structure being adapted to the first anti-slip structure; and / or One of the gasket assembly and the component to be connected is provided with a third anti-slip structure, and the other of the gasket assembly and the component to be connected is provided with a fourth anti-slip structure, wherein the third anti-slip structure is adapted to the fourth anti-slip structure.

10. The bolt assembly according to any one of claims 1 to 9, characterized in that, Along the radial direction of the nut, the length of the bearing portion protruding from the outer surface of the nut is greater than or equal to 2 mm and less than or equal to 6 mm.

11. The bolt assembly according to any one of claims 1 to 9, characterized in that, Along the outer circumferential surface of the nut to the axial direction of the nut, the angle at which the end face of the bearing portion away from the nut is inclined in a direction away from the nut is greater than or equal to 2.5° and less than or equal to 10°.

12. A robot, characterized in that, include: The bolt assembly as described in any one of claims 1 to 11.

Images