WO2024109248A1

WO2024109248A1 - Elastic member, rotation shaft mechanism and electronic device

Info

Publication number: WO2024109248A1
Application number: PCT/CN2023/116650
Authority: WO
Inventors: 杨德森; 臧永强; 霍国亮; 吴崚
Original assignee: 荣耀终端有限公司
Priority date: 2022-11-22
Filing date: 2023-09-04
Publication date: 2024-05-30
Also published as: CN116677704A

Abstract

An elastic member, a rotation shaft mechanism and an electronic device. The elastic member may be applied to electronic devices such as a mobile phone, a notebook computer, and a wearable device. The elastic member comprises an integrally formed cylinder body (1), the cylinder body comprises at least two suspended beam bodies (10), and the suspended beam bodies are arranged at intervals in the axial direction. Each suspended beam body extends in the circumferential direction, and the local positions of adjacent suspended beam bodies are fixedly connected, so that the cylinder body may elastically deform in the axial direction under the action of an axial force. All the suspended beam bodies are integrally formed and do not need to be assembled, thereby improving the assembly efficiency of the rotation shaft mechanism.

Description

Elastic member, rotating shaft mechanism and electronic equipment

This application claims priority to a Chinese patent application filed with the State Intellectual Property Office of China on November 22, 2022, with application number 202211467145.3, and invention name “An elastic part, a rotating shaft mechanism and an electronic device”, the entire contents of which are incorporated by reference in the embodiments of this application.

Technical Field

The embodiments of the present application relate to the field of electronic products, and in particular to an elastic member, a rotating shaft structure and an electronic device.

Background technique

An electronic device such as a laptop computer has a display side and a keyboard side rotatably connected via a shaft structure, wherein a concave cam shaft is a commonly used shaft structure. Please refer to FIG1 , which is a schematic diagram of the structure of a disc spring assembly used in a concave cam shaft in the prior art. The disc spring assembly provides an axial force in the concave cam shaft, that is, when the concave wheel and the cam of the concave cam shaft rotate relative to each other, the disc spring assembly is compressed, and the disc spring assembly generates an axial elastic force to press the relative surfaces of the concave wheel and the cam to generate damping, thereby enabling the two parts connected by the concave cam shaft to be at a predetermined angle.

As can be seen from Figure 1, the disc spring assembly is formed by assembling multiple disc springs. Figure 1 shows that the disc spring assembly includes 5 disc springs. The specific number of disc springs depends on the axial elastic force required by the actual product. Each disc spring has a front side and a back side. All disc springs are assembled through single-layer front and back, double-layer front and back, or other schemes to form an integral installation in the concave cam shaft. Regardless of the assembly scheme adopted by the disc spring assembly, it is necessary to distinguish the front and back and assemble them in sequence. Manual assembly is inefficient and prone to errors. It is necessary to manually distinguish the front and back one by one and pinch them into place. When the number of disc springs required increases to more pieces, the assembly efficiency is lower.

Therefore, how to overcome the above-mentioned defects has always been a technical problem that technicians in this field have been concerned about.

Summary of the invention

The embodiments of the present application provide an elastic member, a rotating shaft structure and an electronic device that do not require assembly and meet usage requirements.

In the first aspect, the embodiment of the present application provides an elastic member, which can be used in the rotating shaft mechanism of an electronic device to provide an axial force that generates damping. The electronic device can be a laptop computer. The elastic member includes an integrally formed cylinder body, which has a central through hole. The material of the cylinder body can be an elastic metal, which can be integrally formed by machining or casting or other processes. The cylinder body includes at least two suspended beams, each of which is arranged at intervals in the axial direction, and each of which extends in the circumferential direction. The local positions of adjacent suspended beams are fixedly connected so that under the action of the axial force, the cylinder body can be elastically deformed in the axial direction. The elastic member in the present application is an integrally formed cylinder body. By arranging the suspended beams connected in sequence on the cylinder body, the axial elastic deformation of the cylinder body can be achieved. Each suspended beam body is integrally formed without assembly and can be installed on the core shaft at one time, thereby improving the assembly efficiency of the rotating shaft mechanism.

In addition, each disc spring may have different stiffness due to different materials, thicknesses, and shapes, resulting in obvious overall differences after assembly, uneven yield levels, and large differences in the consistency experience of the same product. The elastic parts defined in this application can rely on the long life range of the flexible material itself (estimated to be about 100,000 times), provide a longer-lasting and more stable shaft torque experience, and improve the experience consistency of electronic devices.

Based on the first aspect, the present application also provides a first specific implementation of the first aspect: all gaps formed between adjacent suspended beams include a first gap and a second gap. When the cylinder body is subjected to an axial force, the first gap is deformed first, and when the axial force is greater than a predetermined value, the second gap is deformed. In this example, by setting the first gap and the second gap to have different sizes or shapes, a variable stiffness elastic structure can be achieved in which the first gap is deformed first and then the second gap is deformed. The first gap and the second gap are located at different axial positions, that is, they can be arranged in different cross sections perpendicular to the axis.

Based on the first aspect or the first specific embodiment, the present application also provides a second specific implementation of the first aspect: the barrel body includes a first barrel portion and a second barrel portion located at two axial ends, both of which are annular structures, each suspended beam body is located between the first barrel portion and the second barrel portion, the first barrel portion and the second barrel portion are connected to form a whole through each suspended beam body, and the suspended beam bodies located at the two axial ends of each suspended beam body can be fixedly connected to the barrel portion on the corresponding side, and the suspended beam body located on the outside is usually fixedly connected to the barrel portion on the corresponding side through two or more circumferentially uniformly arranged connecting bodies. The outer end surfaces of the first barrel portion and the second barrel portion can be matched and designed according to the structure in contact with them, which can optimize the overall force of the barrel body and facilitate the barrel body to be uniformly compressed along the axial direction. In addition, the axial width of the first barrel portion and the second barrel portion can be greater than that of each suspended beam body, so that the stiffness of the elastic member can be appropriately increased.

Based on the second specific implementation manner of the first aspect, the present application also provides a third specific implementation manner of the first aspect: comprising at least one cantilever unit, the cantilever unit comprising a first pillar and a second pillar, both of which have a predetermined axial length, the first pillar is fixedly connected to the first cylindrical portion, the second pillar is fixedly connected to the second cylindrical portion, and in a non-compressed state, the relative ends of the first pillar and the second pillar have a predetermined spacing along the axial direction; the first pillar and the second pillar are both provided with at least one suspended beam body, the suspended beam body is a cantilever beam, one end of the suspended beam body is fixedly connected to the first pillar and the second pillar, and the non-fixed ends of adjacent suspended beam bodies are fixedly connected by a first connecting body.

The cantilever beam structure has a simple cantilever beam structure and is easy to compress and deform.

Based on the third specific implementation of the first aspect, the present application also provides a fourth specific implementation of the first aspect: the first pillar and the second pillar include two side walls arranged in the circumferential direction, and the free ends of all suspended beams on the same side of the first pillar and the second pillar are connected to the same first connector, and the first connector is suspended between the first barrel and the second barrel. In this example, the suspended beams on the same side are connected and fixed to the same first connector, and the molding process is relatively simple.

Based on the third or fourth specific implementation of the first aspect, the present application also provides a fifth specific implementation of the first aspect: each of the two side walls of the first pillar and the second pillar is provided with a suspended beam body, so that each suspended beam body on both sides of the first pillar and the second pillar is compressed and deformed at the same time, avoiding the first pillar and the second pillar from deflecting during axial deformation, maintaining axial compression, improving the smoothness of rotation of the shaft mechanism, improving the feel of use, and avoiding friction between the barrel body and the core shaft, thereby increasing the service life of the elastic member. The free ends of the suspended beam bodies on the same side are connected by an arc segment or a straight segment, the straight segment connection structure is simple, and the arc segment connection can effectively reduce the stress concentration at the connection position of the two suspended beam bodies, thereby increasing the service life of the barrel body.

Based on the third or fourth specific implementation of the first aspect, the present application also provides a sixth specific implementation of the first aspect: the two side walls arranged along the circumferential direction of the first pillar and the second pillar are both provided with two or more suspended beams, and when the number of suspended beams on the side wall of the first pillar or the second pillar is greater than two, the spacing between adjacent suspended beams is equal or unequal. When the spacing between adjacent suspended beams is equal, the tube body forming process of the structure is simple, and each section of the tube body is uniformly deformed during deformation; when the spacing between adjacent suspended beams is not the same, the one with a larger spacing is compressed and deformed first, and the one with a smaller spacing is compressed and deformed later, which is conducive to forming elastic parts with non-equal stiffness to meet the needs of different products and different usage conditions.

Based on the fifth or sixth specific implementation of the first aspect, the present application also provides a seventh specific implementation of the first aspect: each suspended beam has an equal width or a non-equal width along its extension direction, so as to form an equal width between adjacent suspended beams. Or non-uniform spacing. The suspended beam body can be an arc segment, and the two end faces of the arc segment can be planes, which are perpendicular to the axial direction of the tube body. The structural molding process is relatively simple. Of course, the two end faces of the suspended beam body can also be in the form of bending surfaces or wavy surfaces extending along the circumferential direction, forming equal-spaced gaps or non-uniform-spaced gaps between adjacent suspended beam bodies.

The spacing size and form between adjacent suspended beams can be determined according to the applied product to meet different needs.

Based on the seventh specific implementation manner of the first aspect, the present application also provides an eighth specific implementation manner of the first aspect: the suspended beam body located at the inner end of the first pillar and the suspended beam body located at the inner end of the second pillar form a first gap, and in a non-stress state, the first gaps located on both sides of the same pillar are connected through the gap between the first pillar and the second pillar; a second gap is formed between the axially adjacent suspended beam bodies on the first pillar and between the axially adjacent suspended beam bodies on the second pillar, and the maximum axial spacing of the first gap is greater than the maximum axial spacing of the second gap.

In this example, when the elastic member is compressed, the first support and the second support first move closer to each other, and then the suspended beams on the first support and the second support are deformed simultaneously, thereby forming a non-equal stiffness design, which is relatively simple. Of course, the first spacing can be greater than the second spacing, and the second spacing can be greater than the third spacing, and the structural design of the tube body can be further refined, for example, the gap between the suspended beams on the first support and the gap between the suspended beams on the second support can be further designed into different forms to meet various usage requirements.

Based on the eighth specific implementation of the first aspect, the present application also provides a ninth specific implementation of the first aspect: the axially adjacent suspended beams on the same pillar, the pillars connected to the two ends thereof and the first connector form a second through hole, the maximum axial dimension and the maximum circumferential dimension of the first through hole are respectively larger than the maximum axial dimension and the maximum circumferential dimension of the second through hole, the first through hole includes a first gap, and the second through hole is a second gap; the axially adjacent suspended beams on the same pillar, the pillars connected to the two ends thereof and the first connector form a second through hole, the maximum circumferential dimension of the first through hole is larger than the maximum axial dimension of the second through hole. In this example, the size of the first through hole is larger than the second through hole, which makes it easy to achieve sequential deformation, and the parts of the cantilever unit located on both sides of the first through hole can be structures symmetrical about the central axial cross section of the first through hole.

Based on any one of the first to ninth specific embodiments of the first aspect, the present application also provides a tenth specific embodiment of the first aspect: the axial widths of each suspended beam body along its extension direction are equal or unequal, so as to form equal-width or unequal-width gaps between adjacent suspended beam bodies. In other words, the suspended beam body can be an equal-width structure to form equal-width gaps between adjacent suspended beam bodies, and the structure is relatively simple. The suspended beam body is a unequal-width structure, so that different types of gaps other than rectangular can be formed between adjacent suspended beam bodies, thereby achieving stable deformation along the axial direction.

Based on the tenth specific implementation of the first aspect, the present application also provides an eleventh specific implementation of the first aspect: each suspended beam body includes a first section and a second section connected to each other, and the closer the first section and the second section are to the connection position between the two, the smaller the axial thickness is, so as to form a prismatic gap. The prismatic through hole has a simple structure and relatively high axial deformation stability.

Based on the third to ninth specific embodiments of the first aspect, the present application further provides an eleventh specific embodiment of the first aspect: the number of cantilever units is at least two, and each cantilever unit is evenly arranged along the circumferential direction. The number of cantilever units can be two or three or more, and the cantilever units are evenly arranged along the axial direction, which is conducive to the axial deformation of the barrel body.

Based on the eleventh specific implementation of the first aspect, the present application also provides a twelfth specific implementation of the first aspect: the free ends of the cantilever beams extending toward each other in adjacent cantilever units are fixed to the same first connector. The cantilever units of the elastic member formed in this example can be deformed synchronously along the axial direction to improve the coaxiality of movement.

Based on the second to twelfth specific implementations of the first aspect, the present application also provides the thirteenth specific implementation of the first aspect. A specific implementation method: the projections of the first pillar and the second pillar on the plane perpendicular to the axial direction completely overlap, and the suspended beams on both sides of the first pillar and the second pillar are symmetrically arranged about the axial center plane of the cantilever unit. In this example, the cantilever unit can be symmetrically arranged about the central cross section of the barrel body, and the axial deformation stability is better.

Based on the first specific implementation of the first aspect, the present application also provides a fourteenth specific implementation of the first aspect: each suspended beam body is an annular beam body, the number of annular beam bodies is at least one, and all annular beam bodies divide the space between the first cylinder part and the second cylinder part into N annular gaps, which are: the first annular gap to the Nth annular gap, and at least two spaced second connectors are arranged in each annular gap, the first cylinder part is connected to the adjacent annular beam body through the second connector inside the first annular gap, the second cylinder part is connected to the annular beam body connected to it through the connector in the Nth annular gap, and the adjacent annular beam bodies are connected through the second connector between the two. The annular beam body is an integral structure, and when subjected to axial force, it has better synchronous deformation ability and better stability. Among them, each annular gap can be of equal width or unequal width, and each annular gap can be divided into the same or different sub-gaps. The width of the same sub-gaps can be a gap of equal width or a gap of unequal width.

Based on the fourteenth specific implementation manner of the first aspect, the present application also provides the fifteenth specific implementation manner of the first aspect: the second connectors in each annular gap are evenly arranged circumferentially, and the second connectors inside adjacent annular gaps are staggered, and the projections of the second connectors in adjacent annular gaps in a plane perpendicular to the axial direction at least partially do not overlap; this is conducive to the axial deformation of each layer of annular beams.

Alternatively or alternatively, each of the divided gaps formed by dividing the same annular gap by the second connector is a gap of equal width or a gap of unequal width.

Based on the fifteenth specific implementation of the first aspect, the present application also provides a sixteenth specific implementation of the first aspect: each annular gap has two second connectors, and the central axis planes of the two second connectors in the previous annular gap and the central axis planes of the two second connectors in the next annular gap are at an angle of 80° to 100°. In one example, the central axis planes of the two second connectors in the previous annular gap and the central axis planes of the two second connectors in the next annular gap are at an angle of 90°.

Based on the first aspect and the first to sixteenth specific embodiments, the present application further provides a second specific embodiment of the first aspect: the barrel body is a cylindrical barrel. The cylindrical barrel can improve the smoothness of the rotation of the shaft structure.

In the second aspect, the present invention also provides a shaft structure for realizing relative rotation between a first component and a second component. The shaft structure includes a core shaft for fixing to the first component and a rotating member for fixing to the second component. The rotating member is rotatably connected to the core shaft. The shaft structure also includes a concave-convex assembly and an elastic member of any of the above items. The sleeve is sleeved on the core shaft. When the core shaft and the rotating member rotate relative to each other, the concave-convex assembly can compress the elastic member to produce axial deformation so that the angle between the first component and the second component is set.

In a third aspect, the present invention further provides an electronic device, comprising a first component, a second component and any one of the above-mentioned hinge structures, wherein the first component and the second component are rotationally connected via the hinge structure to achieve relative rotation.

The electronic device and the rotating shaft structure of the present application include the above-mentioned elastic member, and therefore also have the above-mentioned technical effects of the elastic member.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG1 is an exploded schematic diagram of a disc spring in a concave cam type rotating shaft of the prior art;

FIG2 is a schematic diagram of a shaft structure provided by an embodiment of the present application applied to an electronic device;

FIG3 is a schematic diagram of a rotating shaft structure provided in a first embodiment of the present application;

FIG4 is an exploded schematic diagram of FIG3 ;

FIG5 is a schematic diagram of the structure of an elastic member in the first example of the present application;

FIG6 is an expanded view of the elastic member shown in FIG5 after being separated along line L;

FIG7 is a schematic diagram of the structure of an elastic member in the first example of the present application;

FIG8 is an expanded view of the elastic member shown in FIG7 after being separated along line L;

FIG9 is a schematic structural diagram of an elastic member in a third example of the present application;

FIG10 is a schematic diagram of the direction A of FIG9 ;

FIG11 is a schematic diagram of FIG9 in the direction of B;

FIG12 is a schematic diagram of the structure of the elastic member in FIG10 after being separated and unfolded along line L;

FIG13 is a schematic structural diagram of an elastic member in a fourth example of the present application;

FIG14 is a schematic diagram of the elastic member shown in FIG13 in the direction of A;

FIG15 is a schematic diagram of the structure of the elastic member in FIG13 after being separated and unfolded along line L;

FIG16 is a schematic structural diagram of an elastic member in a fifth example of the present application;

FIG. 17 is a schematic diagram of the structure of the elastic member shown in FIG. 16 after being separated and unfolded along line L. FIG.

The one-to-one correspondence between the reference numerals and component names in FIGS. 1 to 17 is as follows:
1 cylinder body; 1-1 first cylinder body portion; 1-2 second cylinder body portion; 11 first pillar; 12 second pillar; 10 suspended beam body; 10a first section; 10b second section; 101 second through hole; 102 first through hole; 103 gap; 13 first connector; 14 second connector; 151 first annular gap; 152 second annular gap; 153 third annular gap; 154 fourth annular gap; 155 fifth annular gap; 156 sixth annular gap; 157 seventh annular gap; 158 eighth annular gap; 1511 first sub-gap; 1521 second sub-gap; 1531 third sub-gap; 1541 fourth sub-gap; 1551 fifth sub-gap; 1561 sixth sub-gap; 1571 seventh sub-gap; 1581 eighth sub-gap.
2 spindle; 3 second bracket; 4 first bracket; 5 cam; 6 cam; 7 locking nut; 8 friction plate

Specific embodiments

Aiming at the technical problems that the disc spring assembly used in the concave cam type rotating shaft mentioned in the background technology is cumbersome to assemble and easy to make mistakes during assembly, resulting in low assembly efficiency, this application has conducted in-depth research and proposed an elastic member that can improve assembly efficiency while meeting the use function of the concave cam type rotating shaft. In other words, the elastic member can provide axial force and can replace the disc spring in the background technology to be applied to the concave cam type rotating shaft.

In the description of this application, it should be noted that the terms "inside", "outside", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the technology concisely, and do not indicate or imply that the device or element referred to must have a specific orientation, specific orientation structure and operation, and therefore cannot be understood as a limitation on the present invention.

In the following, the terms "first", "second", etc. are used only for descriptive purposes and are not to be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Thus, the features defined as "first", "second", etc. may explicitly or implicitly include one or more of the features.

In order to enable those skilled in the art to better understand the technical solution of the present invention, the present invention is further described in detail below in conjunction with the accompanying drawings and specific embodiments.

The hinge structure provided in the embodiment of the present application can be applied to electronic devices. Of course, the hinge structure of the present application can also be applied to sliding doors, folding machine hinges, accessory hinges, etc. The electronic device can be a mobile phone, a wearable device, a vehicle-mounted device, an augmented reality (AR)/virtual reality (VR) device, a laptop computer, an ultra-mobile personal computer (UMPC), a netbook, The present invention may be a mobile terminal such as a personal digital assistant (PDA), or a professional shooting device such as a digital camera, a SLR camera/micro-single camera, a sports camera, a gimbal camera, a drone, etc. The embodiments of the present application do not limit the specific type of the electronic device. For ease of understanding, the electronic device is described below as a laptop computer.

The embodiment of the present application provides a hinge structure, which is used to realize relative rotation of a first component and a second component. The first component and the second component can be any components that need to be relatively rotated, and can be two parts of an electronic device that are rotatably connected. For example, one of the first component and the second component can be the display side of a notebook, and the other can be the keyboard side of the notebook. Of course, one of the first component and the second component can also be the first display side of a foldable mobile phone, and the other can be the second display side of the foldable mobile phone. As long as the electronic device has two components that rotate relatively, the hinge structure in this embodiment can be used to realize rotation.

Please refer to FIG. 2 , which is a schematic diagram of a rotating shaft structure provided in an embodiment of the present application applied to an electronic device, wherein A in FIG. 1 indicates the installation position of the rotating shaft structure.

The electronic device includes a first component 100 and a second component 200 that rotate relative to each other. FIG2 shows that the electronic device is illustrated by taking a laptop computer as an example. FIG1 shows that the first component 100 of the electronic device is the display side of the laptop computer, and the second component 200 is the keyboard side of the laptop computer. The hinge structure 300 realizes the rotational connection between the display side and the keyboard side.

Please refer to Figures 3 and 4, Figure 3 is a schematic diagram of the shaft structure provided by the first embodiment of the present application, and Figure 4 is an exploded schematic diagram of Figure 3. In Figure 3, F represents the force of the elastic member on the concave wheel and the cam, and the arrow represents the direction of F.

The rotating shaft structure provided in the present application includes a core shaft 2, a cam 6, a concave wheel 5, a friction plate 8, a locking nut 7, a first bracket 4, a second bracket 3 and an elastic member, wherein the relative surfaces of the cam and the concave wheel 5 are both concave and convex surfaces, one of which can rotate with the core shaft 2, and the other rotates circumferentially relative to the core shaft 2 and does not rotate with the core shaft 2. Figure 4 shows that the cam 6 rotates with the core shaft 2, the concave wheel 5 is fixed to the first bracket 4 and cannot rotate with the core shaft 2, the second bracket 3 is fixedly connected to the core shaft 2, and the first bracket 4 is connected to the concave wheel 5.

When specifically applied to electronic devices, one of the first bracket 4 and the second bracket 3 is fixed to the first component 100 of the electronic device, and the other is fixed to the second component 200 of the electronic device. In this way, when the core shaft 2 rotates, it can drive one of the first component 100 and the second component 200 to rotate relative to the other. In Figure 2, the core shaft 2 is fixed to the keyboard side of the laptop computer, and the first bracket 4 is fixed to the display side of the laptop computer. Obviously, the core shaft 2 is fixed to the display side of the laptop computer, and the first bracket 4 is fixed to the keyboard side of the laptop computer.

When the core shaft 2 drives the second bracket 3 to rotate relative to the first bracket 4, the cam 5 and the cam 6 rotate relative to each other. Since the relative contact surfaces of the two are convex and concave surfaces, the axial relative positions of the cam 5 and the cam 6 will change during the rotation, thereby generating different degrees of axial compression force on the elastic member, and the elastic member will have different degrees of axial deformation. Under the action of the axial restoring force of the elastic member, a certain damping force can also be formed between the cam 5 and the cam 6, so that the first component 100 and the second component 200 are at a predetermined angle position.

The elastic member of the rotating shaft structure in the present application includes an integrally formed cylinder body 1, the cylinder body 1 having a central through hole, and the cylinder body 1 is sleeved on the core shaft 2 through the central through hole. The cylinder body 1 can be a metal part, such as a metal material with elasticity, and the cylinder body 1 can be integrally formed by machining or casting, etc., and of course, it can also be integrally formed by other methods. The cylinder body 1 can be a cylindrical cylinder, and the cross-sections of the outer surface and the inner surface are both circular holes. Of course, the outer surface of the cylinder body 1 can also be a polygonal structure, as long as it does not affect the use of the elastic member in the corresponding mechanism.

The cylinder body 1 in the present application includes at least two suspended beams 10, each suspended beam 10 is arranged at intervals in the axial direction, and the suspended beams 10 extend in the circumferential direction, and gaps are formed between adjacent suspended beams 10. When the cylinder body 1 is a cylindrical cylinder, the suspended beam 10 can be an arc segment, and the cylinder body 1 has at least two arc segments arranged at intervals in the axial direction. In the present application, the local positions of adjacent suspended beams 10 are fixedly connected, and the local connection positions can be one, two, or more than two. When an axial force is applied, the cylinder body 1 can be elastically deformed in the axial direction.

According to the axial extrusion force during use, the selected material, the wall thickness of the cylinder body 1 and the length of the suspended beam 10 are comprehensively calculated so that the cylinder body 1 can generate sufficient axial extrusion force, and the entire cylinder body 1 is always in the elastic deformation zone during the extrusion process and will not undergo plastic deformation. The problems of plastic deformation and elastic force attenuation in the disc spring technical solution will not occur, thereby increasing the service life of the rotating shaft mechanism with the elastic member of the present application.

Compared with using disc springs to provide axial force, the elastic member in the present application is an integrally formed cylinder body 1. By arranging suspended beams 10 connected in sequence on the cylinder body 1, axial elastic deformation of the cylinder body 1 can be achieved. Each suspended beam 10 is integrally formed and does not require assembly, and can be installed on the core shaft at one time, thereby improving the assembly efficiency of the rotating shaft mechanism.

The elastic member in the present application can be an equal stiffness structure or a non-equal stiffness structure. All gaps formed between adjacent suspended beams 10 in the elastic member in the present application include a first gap and a second gap, that is, the gap formed between a part of adjacent suspended beams 10 is the first gap, and the gap formed between another part of adjacent suspended beams 10 is the second gap. When the cylinder body 1 is subjected to an axial force, the first gap is deformed first, and when the axial force is greater than a predetermined value, the second gap is deformed again. In this example, the first gap and the second gap are set to structures of different sizes or shapes. For example, the axial size and circumferential size of the first gap can be larger than the axial size and circumferential size of the second gap. In this way, a variable stiffness elastic member can be realized in which the first gap is deformed first and then the second gap is deformed to meet the needs of different structures.

The barrel body 1 in the present application includes a first barrel portion 1-1 and a second barrel portion 1-2 located at two axial ends, each suspended beam 10 is located between the first barrel portion 1-1 and the second barrel portion 1-2, and the first barrel portion 1-1 and the second barrel portion 1-2 are connected to form a whole through each suspended beam 10, and the suspended beams 10 located at two axial ends in each suspended beam 10 can be fixedly connected to the barrel portion on the corresponding side. The first barrel portion 1-1 and the second barrel portion 1-2 are annular structures, and their widths along the axial direction can be greater than the width of the suspended beam 10. The first barrel portion 1-1 and the second barrel portion 1-2 can be designed as a structure that cooperates with and abuts against an external component. By abutting against the external component by the first barrel portion 1-1 and the second barrel portion 1-2 of the annular structure, the overall force of the barrel body 1 can be optimized, which is conducive to the barrel body 1 being uniformly compressed along the axial direction.

Please refer to Figures 5 and 6. Figure 5 is a schematic diagram of the structure of the elastic member in the first example of the present application, and Figure 6 is an expanded diagram of the elastic member shown in Figure 5 after being separated along line L.

In the present application, the cylinder body 1 includes a cantilever unit, and the number of cantilever units can be one, two, or more than two. The number of cantilever units depends on the specific use environment, as long as it meets the use requirements. The cantilever unit includes a first pillar 11 and a second pillar 12, both of which have a predetermined axial length. The first pillar 11 is fixedly connected to the first cylinder part 1-1, and the second pillar 12 is fixedly connected to the second cylinder part 1-2. In a non-compressed state, the first pillar 11 and the second pillar 12 have a predetermined spacing H at their relative ends along the axial direction; the first pillar 11 and the second pillar 12 can have roughly the same shape and structure, but of course they can also be different. The first pillar 11 and the second pillar 12 are both provided with at least one suspended beam 10, and the suspended beam 10 The cantilever beam has one end of a cantilever beam body 10 fixedly connected to a first support 11 and a second support 12, and the non-fixed ends of adjacent cantilever beam bodies 10 are fixedly connected via a first connector. The cantilever beam has a simple structure, and when axially compressed, each cantilever beam is easily elastically deformed.

The first pillar 11 and the second pillar 12 include two side walls arranged in the circumferential direction. The first pillar 11 and the second pillar 12 may only have one side wall provided with a cantilever beam. Of course, the first pillar 11 and the second pillar 12 may have cantilever beams on both sides. Figures 5 to 8 show specific examples in which cantilever beams are provided on both sides of the first pillar 11 and the second pillar 12. The provision of cantilever beams on both sides is conducive to uniform circumferential deformation of the cylinder body 1 to avoid eccentricity.

In the first example, only one cantilever beam is disposed on both side walls of the first pillar 11 and the second pillar 12. Please refer to Figures 5 and 6 to understand that the free ends of the cantilever beams on the same side are connected by a first connector. The shape of the first connector can be in various forms, such as an axially extending straight section, or an arc section, wherein the diameter of the arc section can be greater than the spacing between axially adjacent cantilever beam bodies 10, which is conducive to elastic deformation between adjacent cantilever beams. The structure of connecting adjacent cantilever beam bodies 10 by straight sections is relatively simple.

Figures 5 and 6 show examples in which the suspended beam body 10 is an arc-shaped body of equal width. The equal-width structure is relatively simple, the processing technology is relatively simple, and the production cost is low. Of course, the suspended beam body 10 can also be an arc-shaped body of non-equal width along its extension direction, as shown in Figures 7 and 8.

Please refer to Figures 7 to 8, Figure 7 is a schematic diagram of the structure of the elastic member in the first example of the present application, and Figure 8 is an expanded diagram of the elastic member shown in Figure 7 after being separated along line L.

In the second example, two or more cantilever beams 10 are disposed on both side walls of the first pillar 11 and the second pillar 12. FIG. 6, FIG. 7 and FIG. 8 show a specific example in which the number of cantilever units is two, and each side wall of the first pillar 11 and the second pillar 12 is provided with two cantilever beams 10, and the two cantilever units are symmetrical about line S2. Of course, the number of cantilever beams 10 on each side wall of the first pillar 11 and the second pillar 12 is not limited to that shown in the accompanying drawings, and may be three or more. Similarly, the number of cantilever units is not limited to two, and may be three or more. Each cantilever unit is arranged at intervals along the circumferential direction, which is conducive to the coaxial compression deformation of each part of the barrel body 1, and the gap 103 between adjacent cantilever units can be reasonably selected.

In the second example, the maximum axial distance between the suspended beams 10 axially adjacent to each other on the first pillar 11 and the second pillar 12 is the first spacing H, the suspended beams 10 located at the inner end of the first pillar 11 and the suspended beams 10 located at the inner end of the second pillar 12 form a first gap, and in a non-stressed state, the first gaps located on both sides of the same pillar are connected through the gap between the first pillar and the second pillar to form a first through hole 102; a second gap (second through hole 101 in FIG. 7 ) is formed between the suspended beams 10 axially adjacent to each other on the first pillar 11 and between the suspended beams 10 axially adjacent to each other on the second pillar 12, and the maximum axial spacing H of the first gap is greater than the maximum axial spacing h of the second gap. The maximum spacing of the second through holes 101 between the suspended beams 10 axially adjacent to each other on the first pillar 11 is the second spacing h, and the maximum spacing of the suspended beams 10 axially adjacent to each other on the second pillar 12 is also the second spacing h, and the first spacing H is greater than the second spacing h. In this way, during axial compression, the space (first through hole 102) enclosed by the first pillar 11 and the second pillar 12 and the adjacent suspended beams 10 is compressed and deformed first, and then the second through hole 101 between the adjacent suspended beams 10 on the first pillar of the tube is deformed to achieve the variable stiffness requirement. Among them, the maximum spacing between the second through hole 101 and the first through hole 102 can be located on the same axis S4. Of course, at least two rows of second through holes can also be arranged along the axial direction, and the second through holes 101 in the same row are located in the same cross section, and the transverse center lines S1 of the second through holes 101 in the same row are collinear. The first through hole 102 can be a structure symmetrically arranged along the transverse center S of the tube body 1.

In the present application, the structures of the first pillar 11 and the second pillar 12 can be completely identical. The first pillar 11 and the second pillar 12 are arranged opposite to each other, and their projections inside the plane perpendicular to the axial direction completely overlap. The cantilevered beam body 10 on the two side walls of the first pillar 11 and the second pillar 12 can be symmetrically arranged about the axial center plane S3 of the cantilever unit. Please refer to Figure 6 for the position of the axial center plane.

In the present application, the suspended beams 10 arranged in the axial direction are arranged in parallel and have the same size and shape. The spacing between adjacent suspended beams 10 on the same pillar can be the same. Of course, the spacing between adjacent suspended beams 10 on the same pillar can also be different, that is, the position with a larger axial spacing can be deformed first during axial compression, and the position with a smaller axial spacing can be compressed and deformed later, so as to achieve variable stiffness of the cylinder body 1. Of course, the gap formed between adjacent cantilever beams can be a gap of equal width, as shown in the examples of Figures 5, 6, 14 and 15, and of course it can also be a gap of non-equal width, as shown in the examples of Figures 7 to 12 and 16.

Please refer to Figures 9 to 12, Figure 9 is a schematic diagram of the structure of the elastic member in the third example of the present application; Figure 10 is a schematic diagram of the A direction of Figure 9; Figure 11 is a schematic diagram of the B direction of Figure 9; Figure 12 is a schematic diagram of the structure of the elastic member in Figure 10 after being separated and unfolded along the L line.

In the third example, the number of cantilever units is at least two, and the free ends of the cantilever beams extending toward each other in the two cantilever units are fixed to the same first connector. Please refer to Figures 9 and 12 for understanding. Figure 9 shows a specific example with two cantilever units, and the free ends of the cantilever beams on the adjacent side walls of the two first pillars 11 and the adjacent side walls of the two second pillars 12 are connected to the same first connector 13. The barrel body 1 of this structure has high rigidity and high axial stability during deformation, and the free ends of the cantilever beams on the same side of the two cantilever units are connected to the same first connector 13 and can also withstand large axial elastic forces.

In the present application, the axially adjacent suspended beams 10 on the same pillar and the pillars connected to the two ends thereof and the first connector 13 form a second through hole 101, and the maximum dimension of the second through hole 101 along the circumferential direction is greater than the maximum dimension of the second through hole 101 along the axial direction. In the present application, the above-mentioned structural cylinder body 1 is prone to deformation, and has good axial stability during deformation. The edge position of the second through hole 101 extending along the circumferential direction can be set to an arc or rounded connection to reduce the stress concentration phenomenon when this position is deformed, thereby increasing the service life of the cylinder body 1.

The second through hole 101 may have a variety of shapes, such as an ellipse, a circle or an N-gon, the N-gon may be a triangle, a quadrilateral or a pentagon or a polygon with more than five sides, and the adjacent side walls of each polygon are connected by an arc. A specific example of the second through hole 101 is given below, and those skilled in the art should understand that the shape of the second through hole 101 is not limited to the description herein, and may also be other structures.

In the present application, along its circumferential extension direction, each suspended beam body 10 includes a first section 10a and a second section 10b that are connected. The closer the first section 10a and the second section 10b are to the connection position between the two, the smaller the axial thickness is. In this way, the second through hole 101 formed by adjacent suspended beam bodies 10 can be prismatic. The through hole of the prismatic structure can meet both higher stiffness requirements and greater elasticity requirements, and the service life of the tube body 1 is relatively high.

Please refer to Figures 13 to 17, Figure 13 is a schematic diagram of the structure of the elastic member in the fourth example of the present application; Figure 14 is a schematic diagram of the elastic member shown in Figure 13 in the direction of A; Figure 15 is a schematic diagram of the structure of the elastic member described in Figure 13 after being separated and unfolded along the L line; Figure 16 is a schematic diagram of the structure of the elastic member in the fifth example of the present application; Figure 17 is a schematic diagram of the structure of the elastic member shown in Figure 16 after being separated and unfolded along the L line.

In the fourth example, each suspended beam 10 is an annular beam, and the number of the annular beams is at least one. All the annular beams divide the space between the first cylinder part 1-1 and the second cylinder part 1-2 into N annular gaps, which are: From the annular gap to the N-shaped gap, as shown in Figures 13, 14 and 15, the number of annular beam bodies is 7, dividing the first cylindrical body 1-1 to the second cylindrical body 1-2 into eight annular gaps, namely: the first annular gap 151, the second annular gap 152, the third annular gap 153, the fourth annular gap 154, the fifth annular gap 155, the sixth annular gap 156, the seventh annular gap 157 and the eighth annular gap 158. Figures 16 and 17 show that the number of annular beam bodies is 4, dividing the first cylindrical body 1-1 to the second cylindrical body 1-2 into five annular gaps. The number of annular beam bodies is not limited to the above number, and can also be other numbers.

In the present application, at least two second connectors 14 are arranged in each annular gap, the first cylinder portion 1-1 is connected to the adjacent annular beam body through the second connector 14 inside the first annular gap, the second cylinder portion 1-2 is connected to the annular beam body connected to it through the connector in the Nth annular gap, and the adjacent annular beam bodies are connected through the second connector between them. The second connectors 14 in the same annular gap can be two, three or more. In combination with Figures 13 and 15, in the specific example of two second connecting bodies 14 being arranged in the same annular gap, the first annular gap 151 is divided into two first sub-gaps 1511 by the two second connecting bodies 14, the second annular gap 152 is divided into two second sub-gaps 1521, the third annular gap 153 is divided into two third sub-gaps 1531, the fourth annular gap 154 is divided into two fourth sub-gaps 1541, the fifth annular gap 155 is divided into two fifth sub-gaps 1551, the sixth annular gap 156 is divided into two sixth sub-gaps 1561, the seventh annular gap 157 is divided into a seventh sub-gaps 1571, and the eighth annular gap 158 is divided into two eighth sub-gaps 1581.

Each gap can be of equal width, or of course, of unequal width, that is, the gaps in the same layer can be of the same shape and size, or different. Furthermore, the gaps in different layers can be of the same shape and size, or different. Figures 13 to 15 show specific examples of equal axial widths of the gaps, and Figures 16 and 17 show specific examples of unequal axial widths of the same gap. From the figure, it can be seen that the gaps in this example are waist-shaped structures with wide ends and narrow in the middle.

In the embodiment of the present application, the second connectors in each annular gap are evenly arranged in the circumferential direction, and the second connectors 14 inside adjacent annular gaps are staggered, and the projections of the second connectors 14 in adjacent annular gaps in a plane perpendicular to the axial direction at least partially do not overlap; Figures 13 to 17 show schematic diagrams of two second connectors in the same annular gap being evenly arranged in the circumferential direction.

The annular beam body is an integral structure, and when subjected to axial force, it has better synchronous deformation ability and better stability.

The included angle between the central axis planes of the two second connectors in the previous annular gap and the central axis planes of the two second connectors in the next annular gap is 80° to 100°. The figure shows a specific example in which the included angle between the central axis planes of the second connectors of two adjacent layers is 90°.

The hinge mechanism and the electronic device in the embodiments of the present application have the elastic member mentioned above in the present application, and therefore also have the above technical effects of the elastic member.

The electronic device in the embodiment of the application includes the hinge structure of the above embodiment, and therefore also has the above technical effects of the hinge structure.

The principles and implementation methods of the embodiments of the present application are described by using specific examples in the embodiments of the present application. The description of the above embodiments is only used to help understand the methods and core ideas of the embodiments of the present application. It should be pointed out that for ordinary technicians in this technical field, without departing from the principles of the embodiments of the present application, several improvements and modifications can be made to the embodiments of the present application, and these improvements and modifications also fall within the scope of protection of the claims of the embodiments of the present application.

Claims

An elastic part, characterized in that it includes an integrally formed cylinder body with a central through hole, the cylinder body includes at least two suspended beam bodies, each of the suspended beam bodies is arranged at intervals along the axial direction, and each of the suspended beam bodies extends along the circumferential direction, and the local positions of adjacent suspended beam bodies are fixedly connected so that under the action of axial force, the cylinder body can undergo elastic deformation along the axial direction.
The elastic member as described in claim 1 is characterized in that all gaps formed between adjacent suspended beam bodies include a first gap and a second gap, and when the tube body is subjected to an axial force, the first gap is deformed first, and when the axial force is greater than a predetermined value, the second gap is deformed again.
The elastic member as described in claim 1 or 2 is characterized in that the cylinder main body includes a first cylinder part and a second cylinder part located at both ends of the axial direction, both of which are annular structures, each of the suspended beams is located between the first cylinder part and the second cylinder part, the first cylinder part and the second cylinder part are connected to form a whole through each of the suspended beams, and the suspended beams located at both ends of the axial direction in each of the suspended beams can be fixedly connected to the cylinder part on the corresponding side.
The elastic member as described in claim 3 is characterized in that it includes at least one cantilever unit, and the cantilever unit includes a first pillar and a second pillar, both of which have a predetermined axial length, the first pillar is fixedly connected to the first cylindrical portion, and the second pillar is fixedly connected to the second cylindrical portion, and in a non-compressed state, the relative ends of the first pillar and the second pillar have a predetermined spacing along the axial direction; the first pillar and the second pillar are each provided with at least one suspended beam body, the suspended beam body is a cantilever beam, one end of the suspended beam body is fixedly connected to the first pillar and the second pillar, and the non-fixed ends of adjacent suspended beam bodies are fixedly connected by a first connector.
The elastic member as described in claim 4 is characterized in that the first pillar and the second pillar include two side walls arranged in a circumferential direction, and the free ends of all the cantilevered beam bodies located on the same side of the first pillar and the second pillar are connected to the same first connecting body, and the first connecting body is suspended between the first barrel portion and the second barrel portion.
The elastic member according to claim 4 or 5 is characterized in that both side walls of each of the first support and the second support are provided with a cantilever beam body, and the free ends of the cantilever beam bodies on the same side are connected by an arc segment or a straight segment.
The elastic member as described in claim 4 or 5 is characterized in that the two side walls of the first pillar and the second pillar arranged in the circumferential direction are each provided with two or more of the suspended beams, and when the number of the suspended beams on the side walls of the first pillar or the second pillar is greater than two, the spacing between adjacent suspended beams is equal or unequal.
The elastic member as described in any one of claims 4 to 7 is characterized in that the suspended beam body located at the inner end of the first pillar and the suspended beam body located at the inner end of the second pillar form the first gap, and in a non-stressed state, the first gaps located on both sides of the same pillar are connected through the gap between the first pillar and the second pillar; the suspended beam body axially adjacent to the first pillar and the suspended beam body axially adjacent to the second pillar form the second gap, and the maximum axial spacing of the first gap is greater than the maximum axial spacing of the second gap.
The elastic member according to claim 8, characterized in that the first pillar, the second pillar, the suspended beam located at the inner end of the first pillar, and the suspended beam located at the inner end of the second pillar form a first through hole, and the pillars axially adjacent to the suspended beam and connected to the two ends of the suspended beam on the same pillar and the first connecting body form a second through hole, and the maximum axial size and the maximum circumferential size of the first through hole are respectively larger than the maximum axial size and the maximum circumferential size of the second through hole. The first through hole has a large size, and the first through hole includes the first gap, and the second through hole is the second gap.
The elastic member according to any one of claims 1 to 9 is characterized in that the axial widths of each of the suspended beams along the extension direction thereof are equal or unequal, so as to form gaps of equal or unequal widths between adjacent suspended beams.
The elastic member as described in claim 10 is characterized in that each of the suspended beam bodies includes a first section and a second section that are connected, and the closer the first section and the second section are to their connection position, the smaller the axial thickness is, so as to form a prismatic gap between adjacent suspended beam bodies.
The elastic member according to any one of claims 4 to 11, characterized in that the number of the cantilever units is at least two, and the cantilever units are evenly arranged along the circumferential direction.
The elastic member according to claim 12 is characterized in that the free ends of the cantilever beam bodies extending toward each other in adjacent cantilever units are fixed to the same first connecting body.
The elastic member according to any one of claims 3 to 13 is characterized in that the projections of the first pillar and the second pillar in a plane perpendicular to the axial direction completely overlap, and the cantilevered beam bodies on both sides of the first pillar and the second pillar are symmetrically arranged with respect to the axial center plane of the cantilever unit.
The elastic member as described in claim 2 is characterized in that each of the suspended beam bodies is an annular beam body, the number of the annular beam bodies is at least one, and all of the annular beam bodies divide the space between the first cylindrical body portion and the second cylindrical body portion into N annular gaps, which are: the first annular gap to the Nth annular gap, each annular gap is provided with at least two spaced second connectors, the first cylindrical body portion is connected to the adjacent annular beam body through the second connector inside the first annular gap, the second cylindrical body portion is connected to the annular beam body connected to it through the connector in the Nth annular gap, and the adjacent annular beam bodies are connected through the second connector therebetween.
The elastic member according to claim 15, characterized in that the second connectors in each annular gap are uniformly arranged in the circumferential direction, and the second connectors in adjacent annular gaps are staggered, and the projections of the second connectors in adjacent annular gaps in a plane perpendicular to the axial direction at least partially do not overlap;

Alternatively or alternatively, each of the divided gaps formed by dividing the same annular gap by the second connector is a gap of equal width or a gap of unequal width.
The elastic member as described in claim 16 is characterized in that each annular gap has two second connectors, and the angle between the central axis plane of the two second connectors in the previous annular gap and the central axis plane of the two second connectors in the next annular gap is 80° to 100°.
The elastic member according to any one of claims 1 to 17, characterized in that the tube body is a cylindrical tube.
A shaft structure for realizing relative rotation between a first component and a second component, characterized in that the shaft structure comprises a core shaft for fixing to the first component and a rotating member for fixing to the second component, the rotating member being rotatably connected to the core shaft, the shaft structure further comprises a concave-convex assembly and an elastic member according to any one of claims 1 to 18, the sleeve being sleeved on the core shaft, and when the core shaft and the rotating member are relatively rotated, the concave-convex assembly can compress the elastic member to produce axial deformation so as to set an angle between the first component and the second component.
An electronic device, characterized in that it comprises a first component, a second component and the hinge structure according to claim 19, wherein the first component and the second component are rotatably connected via the hinge structure.