WO2023056796A1 - 转轴以及终端设备 - Google Patents

转轴以及终端设备 Download PDF

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Publication number
WO2023056796A1
WO2023056796A1 PCT/CN2022/114629 CN2022114629W WO2023056796A1 WO 2023056796 A1 WO2023056796 A1 WO 2023056796A1 CN 2022114629 W CN2022114629 W CN 2022114629W WO 2023056796 A1 WO2023056796 A1 WO 2023056796A1
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WO
WIPO (PCT)
Prior art keywords
rotating shaft
concave
elastic member
bracket
cam
Prior art date
Application number
PCT/CN2022/114629
Other languages
English (en)
French (fr)
Inventor
杨德森
吴崚
许自宾
霍国亮
Original Assignee
荣耀终端有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 荣耀终端有限公司 filed Critical 荣耀终端有限公司
Priority to EP22871135.4A priority Critical patent/EP4206482A4/en
Priority to US18/249,283 priority patent/US20230400055A1/en
Publication of WO2023056796A1 publication Critical patent/WO2023056796A1/zh

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Classifications

    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F1/00—Details not covered by groups G06F3/00 - G06F13/00 and G06F21/00
    • G06F1/16—Constructional details or arrangements
    • G06F1/1613—Constructional details or arrangements for portable computers
    • G06F1/1633—Constructional details or arrangements of portable computers not specific to the type of enclosures covered by groups G06F1/1615 - G06F1/1626
    • G06F1/1675—Miscellaneous details related to the relative movement between the different enclosures or enclosure parts
    • G06F1/1681—Details related solely to hinges
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/10—Arrangements for locking
    • F16C11/103—Arrangements for locking frictionally clamped
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F1/00—Details not covered by groups G06F3/00 - G06F13/00 and G06F21/00
    • G06F1/16—Constructional details or arrangements
    • G06F1/1613—Constructional details or arrangements for portable computers
    • G06F1/1615—Constructional details or arrangements for portable computers with several enclosures having relative motions, each enclosure supporting at least one I/O or computing function
    • G06F1/1616—Constructional details or arrangements for portable computers with several enclosures having relative motions, each enclosure supporting at least one I/O or computing function with folding flat displays, e.g. laptop computers or notebooks having a clamshell configuration, with body parts pivoting to an open position around an axis parallel to the plane they define in closed position
    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04M—TELEPHONIC COMMUNICATION
    • H04M1/00—Substation equipment, e.g. for use by subscribers
    • H04M1/02—Constructional features of telephone sets
    • H04M1/0202—Portable telephone sets, e.g. cordless phones, mobile phones or bar type handsets
    • H04M1/0206—Portable telephones comprising a plurality of mechanically joined movable body parts, e.g. hinged housings
    • H04M1/0208—Portable telephones comprising a plurality of mechanically joined movable body parts, e.g. hinged housings characterized by the relative motions of the body parts
    • H04M1/0214—Foldable telephones, i.e. with body parts pivoting to an open position around an axis parallel to the plane they define in closed position
    • H04M1/0216—Foldable in one direction, i.e. using a one degree of freedom hinge

Definitions

  • the present application relates to the technical field of mechanical structures, in particular to a rotating shaft and a terminal device.
  • the present application provides a rotating shaft, which includes a central shaft, a first bracket, a second bracket, an elastic member, and a concave-convex wheel assembly.
  • the first bracket is rotatably mounted on the central shaft; the second bracket is fixedly connected to the central shaft; the elastic member is arranged on the central shaft, the elastic member is a hollow cylinder with an integrated structure, and the cylinder wall of the cylinder is provided with hollow holes;
  • the concave-cam assembly is arranged on the central shaft, and the concave-cam assembly can deform the elastic member; wherein, when the first bracket rotates compared with the second bracket, the concave-cam assembly produces a pressing force acting on the elastic piece so that the hollow-shaped The elastic member is deformed so that a certain angle is formed between the first bracket and the second bracket.
  • the hollow-shaped elastic member with an integrated structure can be assembled to the central shaft at one time, and the installation is simple, thereby improving the installation efficiency.
  • the elastic part replaces the disc spring group composed of multiple disc springs, which fundamentally avoids the problems of low efficiency and high error rate caused by assembling multiple disc springs, and does not need to set up additional automatic assembly equipment.
  • the elastic member with an integrated structure can avoid the use of multiple disc springs in the related art or the spring has torsion fluctuations perpendicular to the axial direction.
  • the elastic member structure of the present application is more conducive to the connection between the first body and the second body. Stability after opening.
  • the elastic member is always in the elastic deformation zone of the elastic member during the process of being deformed by the extrusion force, and no plastic deformation will occur, so the problems of plastic deformation and elastic attenuation of the disc spring in the related art will not occur, and the use of frequency. Furthermore, according to the structure of the elastic member of the present application, it is also possible to design the elastic member to have a constant force characteristic when the extrusion force received by the elastic member exceeds a critical point.
  • the cylinder wall of the elastic member is provided with a plurality of hollow holes and a plurality of connecting ribs, and the plurality of hollow holes and the plurality of connecting ribs are interlaced and arranged at intervals to form the elastic member.
  • the setting of the hollow hole makes the elastic member deform in the axial direction when the elastic member is subjected to the extrusion force in the axial direction.
  • the extension direction of the connecting rib can be any direction, and the connecting rib can make the elastic member remove the shaft In addition to deformation in one direction, deformation can also occur in other directions.
  • the shape of the hollow hole includes at least one of a polygon and an arc.
  • the shape of the hollow is a regular shape, it is beneficial to design and process the elastic member according to the extrusion force that the elastic member needs to receive, and the force of the elastic member along the axial direction of the central axis is uniform .
  • the polygon includes at least one of square, rectangle, rhombus, pentagon, and hexagon; the arc includes at least one of spiral, circle, ellipse, and semicircle.
  • the shape of the hollow is related to the clamping force required by the rotating shaft.
  • the material of the elastic member is selected from one of metal, metal alloy and plastic.
  • the elastic member made of metal or metal alloy has stronger toughness and can be used more frequently.
  • the elastic part made of plastic can be formed by injection molding, and the processing cost is low.
  • the central shaft includes a fixed part fixedly connected, a blocking part and a rod part, and the blocking part is located between the rod part and the fixed part; the second bracket is fixed on the fixed part, and the rod part passes through the first A bracket, concave-convex wheel assembly, elastic member, the first bracket resists on the blocking part.
  • the fixing part is used to fix the second body; the blocking part is used to cooperate with the fixing part, so that the distance between the blocking part and the fixing part remains constant.
  • the squeeze The elastic part is pressed to make the elastic part deform; the rod part is used to connect the elastic part and the concave-convex wheel assembly as a whole.
  • the first bracket includes a first fixing plate, a first through hole is opened on the first fixing plate, the rod part passes through the first through hole, and the first fixing plate abuts against the blocking part.
  • the blocking portion restricts the first fixing plate, so that the first bracket is relatively fixed to the central axis.
  • the concave-cam assembly includes an adjacent concave wheel and a cam, one of the concave wheel and the cam is fixedly connected to the first bracket, and the other of the concave wheel and the cam is fixedly connected to the central shaft.
  • the concave wheel is movably connected to the cam, so that the total width of the concave-cam assembly along the axial direction can be changed to deform the elastic member.
  • a fixing hole is provided on the first fixing plate, the concave wheel includes a concave wheel part and a clamping part connected to each other, the concave wheel part is sleeved on the rod part, and the clamping part is clamped in the fixing hole .
  • the concave wheel is fixedly connected to the first fixing plate through the cooperation of the clamping portion and the fixing hole.
  • the concave wheel portion is provided with a second through hole, and the minimum diameter of the second through hole is larger than the maximum diameter of the rod portion.
  • the rod portion and the concave wheel can rotate relative to each other.
  • the cam is provided with a third through hole, the third through hole is flat, the rod is flat, and the cam is sleeved on the rod.
  • the surface connecting the concave wheel part and the cam includes a connected concave part and a flat grinding area
  • the surface connecting the cam and the concave wheel includes a protruding part
  • the protruding part can be accommodated in the concave part .
  • the concave part of the concave wheel part is adapted to the flat grinding area and the protruding part of the cam.
  • the cam and the concave wheel rotate relatively, and the elastic member reaches a critical point where the extrusion force is a constant force before the protruding portion contacts the flat grinding area.
  • the concave wheel is used to maintain relative stability between the concave wheel and the cam, so that the first body and the second body maintain an opening and closing angle required by the user.
  • the rotating shaft further includes a fixing part, and the fixing part is fixed on a side of the rod part away from the blocking part and abuts against a surface of the elastic part away from the concave-convex wheel assembly.
  • the fixing part is used to cooperate with the blocking part, so that the distance between the fixing part and the blocking part remains constant, and when the total width of the concave-cam assembly changes, the elastic part is squeezed, so that the elastic part is deformed .
  • the rotating shaft also includes a friction plate, the friction plate includes a fourth through hole, the fourth through hole is flat, and the shape of the fourth through hole is adapted to the shape of the rod; the friction plate is located on the fixed part and between the barrier.
  • the distance between the fixing piece and the concave-cam assembly can be reduced, thereby reducing the width of the elastic piece along the axial direction, increasing the reaction force of the elastic piece acting on the concave-cam assembly, and increasing the The frictional force in the axial direction improves the stability when the first body and the second body are opened and closed.
  • the friction plate is located between the concave wheel and the first fixing plate.
  • the surface of the friction plate connected with the concave wheel and the first fixed plate has a certain roughness. Since the concave wheel is fixedly connected with the first fixed plate, the friction plate is fixedly connected with the central shaft, and the setting of the friction plate , to increase the frictional force, which can increase the recovery resistance of the first body or the second body along the direction of gravity, thereby improving the stability of the first body and the second body when opening and closing; it can also reduce the gap between the fixing piece and the concave cam assembly distance, thereby reducing the width of the elastic member along the axial direction, increasing the reaction force of the elastic member acting on the concave-cam assembly, and increasing the frictional force of each element along the surface perpendicular to the axial direction, thereby further enhancing the first body Stability when opening and closing with the second body.
  • the present application provides a terminal device, where the terminal device includes a first body, a second body, and a rotating shaft.
  • the first body is fixedly connected with the first bracket
  • the second body is fixedly connected with the second bracket.
  • FIG. 1 is a schematic diagram of an overall structure of a terminal device provided by an embodiment of the present application.
  • Fig. 2 is a schematic diagram of the overall structure of a rotating shaft including a disc spring set provided by some embodiments of the present application.
  • FIG. 3 is an exploded view of the rotating shaft shown in FIG. 2 .
  • FIG. 4 is a structural schematic view of a plurality of disc springs assembled into the disc spring group shown in FIG. 2 .
  • FIG. 5 is a schematic diagram of the overall structure of a rotating shaft including an elastic member provided by other embodiments of the present application.
  • FIG. 6 is an exploded view of the rotating shaft shown in FIG. 5 .
  • FIG. 7 is an exploded view of the concave cam assembly shown in FIG. 6 .
  • FIG. 8 is an exploded view of another orientation of the concave-cam assembly shown in FIG. 6 .
  • FIG. 9 is a schematic diagram of the overall structure when the concave wheel and the cam in the rotating shaft do not rotate relative to each other.
  • Fig. 10 is a schematic diagram of the overall structure after the concave wheel and the cam in the rotating shaft rotate relative to each other.
  • Fig. 11 is a schematic diagram of the overall structure in which the hollow shape of the rotating shaft is hexagonal.
  • Fig. 12 is a schematic plan view of the hollow shape of the rotating shaft as a quadrilateral.
  • Fig. 13 is a schematic diagram of the overall structure in which the hollow shape of the rotating shaft is spiral.
  • FIG. 14 is a schematic plan view of a rotating shaft with a circular hollow shape.
  • FIG. 15 is a schematic diagram of the structure before deformation (solid line) and after deformation (dotted line) when the hollow shape of the rotating shaft is a hexagon.
  • Fig. 16 is a schematic diagram of the relationship between the extrusion force on the rotating shaft and the deformation in the axial direction.
  • Terminal Equipment 200 first ontology 210 second body 220 shaft 100, 100a The central axis 10, 10a fixed part 11 first piercing 112 blocking part 13 shaft 15 first bracket 20, 20a first fixed plate twenty one first via 212 Fixing hole 214 second fixed plate twenty three second piercing 232 second bracket 30, 30a Disc spring set 40a disc spring 41a concave cam assembly 50, 50a concave wheel 51
  • Notch 512 Second via 5122 Depression 5124 Flat grinding area 5126 Holder 514 cam 53 third via 532 protrusion 534 Elastic 60, 60a, 60b, 60c Fifth via 61 hollow hole 63, 63a, 63b, 63c connecting rib 65, 65a, 65b, 65c Fastener 70 Friction plate 80 Fourth via 81 distance D. width W1, W2 critical point t angle ⁇ extrusion force f
  • connection used in the specification and claims of the present application is not limited to physical or mechanical connection, no matter it is direct or indirect. of. "Up”, “Down”, “Above”, “Bottom”, “Left”, “Right” and so on are only used to indicate the relative positional relationship. When the absolute position of the described object changes, the relative positional relationship is also corresponding Change.
  • the embodiment of the present application provides a terminal device 200, which includes but not limited to computers, mobile phones, doors, Bluetooth headset boxes, glasses cases and other products that need to use the hinge 100.
  • the terminal device 200 is a notebook computer.
  • the terminal device 200 includes a first body 210, a second body 220, and a rotating shaft 100.
  • the rotating shaft 100 connects the first body 210 and the second body 220.
  • the opening and closing angles of the first body 210 and the second body 220 can be changed through the function of the rotating shaft 100. , and maintain the opening and closing angle required by the user.
  • the specific names of the first body 210 and the second body 220 are related to usage scenarios of the rotating shaft 100 .
  • the first body 210 can be a keyboard, and the second body 220 can be a display screen;
  • the terminal device 200 is a door, the first body 210 can be a door frame, and the second body 220 can be a door panel.
  • the foregoing is for illustration only and not for limitation.
  • the rotating shaft 100a includes a central shaft 10a, a first bracket 20a, a second bracket 30a, a disc spring set 40a, and a concave-convex wheel assembly 50a.
  • the first bracket 20a is rotatably arranged on the central shaft 10a
  • the second bracket 30a is fixed on the central shaft 10a
  • the disc spring group 40a is arranged on the central shaft 10a
  • the concave-cam assembly 50a is arranged on the central shaft 10a
  • the concave-cam assembly 50a can cause the disc spring set 40a to deform along the extension direction of the central axis 10a.
  • the first bracket 20 a is used for fixing with the first body 210
  • the second bracket 30 a is used for fixing with the second body 220 .
  • the first bracket 20a is rotatably connected to the second bracket 30a, so that the first body 210 and the second body 220 can be opened and closed.
  • the disc spring group 40a is formed by assembling a plurality of disc springs 41a.
  • Each disc spring 41a is a ring-shaped thin sheet.
  • the thickness of the disc spring 41a can be 0.4mm-0.6mm.
  • the disc spring set 40a is formed by assembling five disc springs 41a.
  • the disc spring 41a has positive and negative points in the process of assembling to form the disc spring set 40a. During the assembling process, the front and the reverse need to be manually assembled alternately, so as to form the disc spring set 40a with elasticity.
  • the inventors of the present application found that manual assembly is inefficient and error-prone. In some usage scenarios, for example, the size of the disc spring 41a is small, it is difficult to distinguish the front and back of the disc spring 41a, or the number of disc springs 41a to be used is large, etc.
  • the terminal device 200 with the rotating shaft 100a is usually used multiple times, so the use of the rotating shaft 100a
  • the frequency is relatively high, and the number of times that the above-mentioned disc spring set 40a can usually be used is limited (for example, 20,000-30,000 times), and there will be a large elastic force attenuation, which will cause a sharp drop in the torque of the rotating shaft 100a, affecting the use of users;
  • the disc spring group 40a is composed of multiple disc springs 41a.
  • the elasticity of the springs is difficult to support the first body 210 or The second body 220 .
  • the external force of the disc spring group 40a or the spring is positively correlated with the deformation, that is, when the magnitude of the external force changes, the deformation of the disc spring group 40a or the spring will change, resulting in a force acting on the first body 210 or the second body 220.
  • the force is unstable.
  • the rotating shaft 100 includes a central shaft 10 , a first bracket 20 , a second bracket 30 , an elastic member 60 and a concave-convex wheel assembly 50 .
  • the first bracket 20 is relatively rotatably connected to the central shaft 10
  • the second bracket 30 is fixedly connected to the central shaft 10
  • the elastic member 60 is arranged on the central shaft 10
  • the elastic member 60 is hollow
  • the concave cam assembly 50 is arranged on the central shaft 10
  • the concave-convex wheel assembly 50 can deform the elastic member 60 .
  • the concave-convex wheel assembly 50 deforms the hollow-shaped elastic member 60 so that a certain angle is formed between the first bracket 20 and the second bracket 30 .
  • the central shaft 10 includes a fixed part 11 fixedly connected, a blocking part 13 and a rod part 15, the blocking part 13 is located between the fixing part 11 and the rod part 15, and the rod part 15
  • the side away from the fixing portion 11 extends outwards, and for convenience of description, the direction in which the rod portion 15 extends is defined as the X-axis direction (ie, the axial direction of the rod portion 15 ).
  • the diameter of the blocking portion 13 is larger than the diameter of the rod portion 15 .
  • the fixing part 11 is in the shape of a flat block, and a first through hole 112 is opened on the fixing part 11 , and the first through hole 112 can cooperate with a nut for fixing the second body 220 .
  • the rod portion 15 passes through the first bracket 20, the concave-cam assembly 50 and the elastic member 60 in sequence, the first bracket 20 is held against the blocking portion 13, the concave-cam assembly 50 is located between the elastic member 60 and the first bracket 20, and the rotating shaft 100
  • the fixing part 70 is located at the end of the rod part 15 so as to fix the first bracket 20, the elastic part 60 and the concave-convex wheel assembly 50 on the rod part 15, so that the fixing part 70 and the first bracket 20 along the X
  • the distance D in the axial direction is fixed.
  • the fixing member 70 is a nut.
  • the fixing method is not limited to fixing with a nut, and may also be bonding or clamping.
  • the first bracket 20 includes a first fixing plate 21 and a second fixing plate 23 , and the first fixing plate 21 and the second fixing plate 23 are fixedly connected.
  • the second fixing plate 23 is disposed on a surface of the first fixing plate 21 and has a certain angle with the first fixing plate 21 .
  • the second fixing plate 23 and the first fixing plate 21 are perpendicular to each other.
  • the angle between the second fixing plate 23 and the first fixing plate 21 is not limited, and can be set as required.
  • the second fixing plate 23 is provided with a second through hole 232 , and the second through hole 232 can cooperate with a nut for fixing the first body 210 .
  • the first fixing plate 21 is provided with a first through hole 212 and a fixing hole 214 .
  • the first through hole 212 runs through two opposite surfaces of the first fixing plate 21 , the first through hole 212 is used for the central axis 10 to pass through, and the first fixing plate 21 abuts against the surface of the blocking portion 13 away from the fixing portion 11 .
  • the fixing hole 214 may be a through hole or a receiving groove. In this embodiment, the fixing hole 214 is a through hole for limiting the concave-cam assembly 50 .
  • the concave cam assembly 50 is sleeved on the rod portion 15 .
  • the concave-cam assembly 50 includes adjacent concave wheels 51 and cams 53 , the surfaces of which the concave wheels 51 and the cams 53 are connected cooperate with each other, and the concave wheels 51 and the cams 53 are movably connected.
  • One of the concave wheel 51 and the cam 53 is fixedly connected with the first bracket 20, and the other of the concave wheel 51 and the cam 53 is fixedly connected with the central shaft 10.
  • the concave wheel 51 and the cam 53 move relative to each other, the concave wheel 51
  • the total width of the cam 53 along the X-axis direction changes, so that a relative pressing force F acts on the elastic member 60 , causing the elastic member 60 to deform.
  • the concave wheel 51 is fixedly connected to the first fixing plate 21
  • the cam 53 is fixedly connected to the rod portion 15
  • the concave wheel 51 includes a concave wheel portion 512 and a clamping portion 514, the clamping portion 514 is connected to the edge area of the concave wheel portion 512 and extends toward the direction of the first fixing plate 21, at least part of the clamping portion 514 is clamped in the fixing hole 214 , so that the concave wheel 51 is fixedly connected with the first bracket 20 .
  • the concave wheel portion 512 defines a second through hole 5122 , and the minimum diameter of the second through hole 5122 is larger than the maximum diameter of the rod portion 15 so that the rod portion 15 and the concave wheel 51 can rotate relative to each other.
  • the cam 53 is provided with a third through hole 532, the third through hole 532 is flat, and the rod 15 is also flat, the third through hole 532 is compatible with the rod 15, the cam 53 is relatively fixed with the rod 15, and the center
  • the cam 53 rotates synchronously with the central shaft 10
  • the flat rod portion 15 and the flat third through hole 532 are provided, and the cam 53 can be fixedly connected with the central shaft 10 through a simple structural design, and It also facilitates the assembly of the rotating shaft 100 .
  • the fixing method of the cam 53 and the central shaft 10 may also be bonding, clamping and the like.
  • the surface of the concave wheel portion 512 connected with the cam 53 includes a connected concave portion 5124 and a flat grinding area 5126
  • the surface of the cam 53 connected with the concave wheel 51 includes a protruding portion 534 .
  • the protruding portion 534 corresponds to the concave portion 5124 , that is, the protruding portion 534 is accommodated in the concave portion 5124 .
  • the number of recessed parts 5124 or protruding parts 534 is related to the angle to be maintained after the first body 210 and the second body 220 are opened to each other.
  • the number of the concave portion 5124 and the protruding portion 534 is not limited.
  • the concave wheel 51 and the cam 53 when the concave wheel 51 and the cam 53 do not rotate relative to each other, the concave wheel 51 and the cam 53 have a total width W1 along the X-axis direction.
  • the protruding portion 534 will gradually rotate relative to the concave wheel 51 along the side wall of the concave portion 5124.
  • the cam 53 and the concave wheel 51 will rotate along the X-axis.
  • the total width W1 in the direction gradually increases. Since the distance D between the fixing member 70 and the first fixing plate 21 is constant, the width of the elastic member 60 gradually decreases, and the pressing force F received by the elastic member 60 gradually increases; Please refer to Fig.
  • the concave wheel 51 is fixedly connected with the first bracket 20, the first bracket 20 is fixedly connected with the first body 210, the cam 53 is fixedly connected with the central shaft 10, and the central shaft 10 is fixedly connected with the second body 220, then the concave wheel 51
  • the relative rotation with the cam 53 synchronously drives the first body 210 and the second body 220 to generate relative rotation, and the relative rotation angle between the first body 210 and the second body 220 can be set as required.
  • the surfaces forming the recessed part 5124 and the protruding part 534 are both arc surfaces.
  • the elastic member 60 is a hollow cylinder, and the elastic member 60 has an integral structure.
  • the center of the elastic member 60 has a fifth through hole 61 for sheathing on the rod portion 15 .
  • the elastic member 60 with integral structure can be assembled on the central shaft 10 at one time, and the installation is simple, thereby improving the installation efficiency.
  • the elastic member 60 replaces the disc spring group 40a composed of multiple disc springs 41a, fundamentally avoiding the problems of low efficiency and high error rate caused by assembling multiple disc springs 41a, and no additional automatic assembly equipment is required.
  • the shape of the hollow can be a regular shape or an irregular shape, and the regular shape includes but is not limited to a polygon (see Figure 11 and Figure 12) or an arc (see Figure 13 and Figure 14), etc., wherein the polygon includes but not
  • the shape is limited to square, rectangle, rhombus, pentagon, hexagon, etc.
  • the arc includes but not limited to spiral, circle, ellipse, or semicircle.
  • the above shapes can be combined with each other.
  • the shape of the hollow is regular, it is beneficial to design and process the elastic member 60 according to the extrusion force F that the elastic member 60 needs to receive, and the force of the elastic member 60 along the X-axis direction is uniform.
  • the tube wall of a hollow elastic member 60 provided in the embodiment of the present application provides a plurality of hollow holes 63 and a plurality of connecting ribs 65, the hollow holes 63 communicate with the fifth through hole 61, and the hollow holes
  • the hole 63 is hexagonal in shape, and a plurality of hollow holes 63 are interlaced with a plurality of connecting ribs 65 and arranged at intervals to form a hollow elastic member 60, so that the cylinder wall of the elastic member 60 forms a honeycomb-like hollow cylinder wall.
  • the tube wall of another hollow elastic member 60a provided in the embodiment of the present application has a plurality of hollow holes 63a and a plurality of connecting ribs 65a, and the hollow holes 63a communicate with the fifth through hole (not shown).
  • the hollow holes 63a are diamond-shaped, and the hollow holes 63a are alternately connected with the connecting ribs 65a and arranged at intervals to form the hollow elastic members 60a.
  • the cylinder wall of another hollow elastic member 60b provided in the embodiment of the present application has a plurality of hollow holes 63b, a plurality of connecting ribs 65b between the hollow holes 63b, the hollow holes 63b and the fifth through hole 61, the hollow holes 63b are spiral, and the hollow holes 63b are interlaced with the connecting ribs 65b, and the hollow elastic members 60b are arranged at intervals.
  • the extension direction of the connecting rib 65b includes extending along the X-axis direction (axial direction) and extending in a direction intersecting with the X-axis direction, wherein, the connecting rib 65b extending along the X-axis direction makes the elastic member 60b , with the possibility of deformation along the direction intersecting the X-axis direction.
  • the wall of another hollow elastic member 60c provided in the embodiment of the present application has a plurality of hollow holes 63c and a plurality of connecting ribs 65c, and the hollow holes 63c communicate with the fifth through hole (not shown).
  • the hollow hole 63c is circular, and a plurality of hollow holes 63c are alternately connected with a plurality of connecting ribs 65c and arranged at intervals to form a hollow elastic member 60c.
  • the hollow shape formed is different.
  • the extending direction of the connecting rib 65 can be in any direction.
  • the connecting rib 65 can make the elastic member 60 deform in other directions besides the axial direction.
  • the connecting ribs 65 forming a hexagon are perpendicular to the extrusion force F, please refer to Figure 16, when the elastic member 60 is subjected to the extrusion force F, it can be compressed along the X-axis direction so that Deformation occurs, and as the extrusion force F increases, the amount of deformation of the elastic member 60 increases; when the extrusion force F received by the elastic member 60 reaches a critical point t (as shown in t in Figure 16), the elastic member 60 is still It can bulge outward along the direction intersecting the X-axis to generate deformation (as shown in dotted line in Figure 15), and the connecting rib 65 of the elastic member 60 can generate deformation in multiple directions (not limited to deformation along the X-axis direction), That is, the concave-cam assembly 50 continues to squeeze the elastic member 60, beyond the critical point t, the deformation of the elastic member 60 includes the deformation along the X-axis direction and the deformation in the direction intersecting the X-axis. According
  • reaching the critical point t that is, the pressing force F experienced by the elastic member 60 becomes a constant force
  • reaching the critical point t that is, the pressing force F experienced by the elastic member 60 becomes a constant force
  • reaching the critical point t that is, the pressing force F experienced by the elastic member 60 becomes a constant force
  • reaching the critical point t that is, the pressing force F experienced by the elastic member 60 becomes a constant force
  • reaching the critical point t that is, the pressing force F experienced by the elastic member 60 becomes a constant force
  • the critical point t of the elastic member 60 has a certain relationship with the hollow shape, the material and thickness of the elastic member 60, the angle ⁇ between the connecting rib 65 and the extrusion force F (please refer to Figure 15), etc., and can be determined according to the elastic
  • the extrusion force F required by the element 60 is comprehensively calculated by the material, wall thickness, hollow shape, etc. selected by the elastic element 60, so that the elastic element 60 can produce a suitable extrusion force F, and it can also be determined according to whether the elastic element 60 needs to achieve a constant force
  • the material, wall thickness, and hollow shape of the elastic member 60 are designed in intervals to realize the function of the rotating shaft 100 when the rotating shaft 100 is applied to a specific terminal device 200 .
  • the elastic member 60 is always in the elastic deformation zone of the elastic member 60 during the process of being deformed by the extrusion force F, and no plastic deformation will occur, so the problems of plastic deformation and elastic attenuation of the disc spring 41a in the related art will not occur. .
  • the range of the constant force interval (that is, the width when the extrusion force F in the direction of deformation in the axial direction in Figure 16 is a constant force) has a certain relationship with the angle ⁇ between the connecting rib 65 and the extrusion force F, and in some implementations
  • the range of the angle ⁇ is 50°-70°
  • the range of the constant force interval is the largest; when the angle ⁇ is less than 50°, the range of the constant force interval varies with the angle
  • the increase of ⁇ increases; when the angle ⁇ is greater than 70°, the range of the constant force interval decreases with the increase of the angle ⁇ .
  • the angle ⁇ between the connecting rib 65 and the extrusion force F can be selected according to the actual application of the rotating shaft, that is, the hollow shape and the arrangement direction of the hollow shape can be selected according to the needs.
  • the elastic member 60 can be made of metal, metal alloy or plastic.
  • the elastic member 60 made of metal or metal alloy has stronger toughness and can be used more frequently.
  • the elastic member 60 made of plastic can be formed by injection molding, and the processing cost is low. In some embodiments, the frequency of use of the elastic member 60 exceeds one hundred thousand times.
  • the rotating shaft 100 also includes a friction plate 80 , and the surface roughness of the friction plate 80 is relatively large.
  • the friction plate 80 includes a fourth through hole 81 , the fourth through hole 81 is flat, the shape of the fourth through hole 81 matches the shape of the rod portion 15 , and the friction plate 80 is fixedly connected to the rod portion 15 .
  • the friction plate 80 is located between the concave wheel 51 and the first fixed plate 21, and the surface connecting the friction plate 80 with the concave wheel 51 and the first fixed plate 21 has a certain roughness, because the concave wheel 51 and the first fixed plate 21
  • the friction plate 80 is fixedly connected with the central shaft 10.
  • the setting of the friction plate 80 can increase the friction force between the friction plate 80 and the adjacent elements (that is, the concave wheel 51 and the first fixed plate 21).
  • the first body 210 or the second body 220 has a recovery tendency along the direction of gravity, and the frictional force is increased. , can increase the recovery resistance of the first body 210 or the second body 220 in the direction of gravity, thereby improving the stability of the first body 210 and the second body 220 when opening and closing.
  • the arrangement of the friction plate 80 can reduce the distance between the fixing member 70 and the concave-cam assembly 50, thereby reducing the width of the elastic member 60 along the X-axis direction, and increasing the reaction of the elastic member 60 to the concave-cam assembly 50
  • the force can also increase the frictional force of each element along the surface perpendicular to the X-axis direction, thereby further improving the stability when the first body 210 and the second body 220 are opened and closed.
  • the concave wheel 51 and the surface adjacent to the friction plate 80 of the first fixed plate 21 can also be provided with grooves or protrusions that are suitable for the surface roughness of the friction plate 80, so that the rotating shaft 100 and the first When the main body 210 or the second main body 220 maintains a certain angle, there is a proper friction force.
  • the friction plate 80 may also be located between the cam 53 and the fixing member 70 , for example, between the fixing member 70 and the elastic member 60 or between the elastic member 60 and the concave cam assembly 50 .
  • the arrangement of the friction plate 80 can reduce the distance between the fixing member 70 and the concave-cam assembly 50, thereby reducing the width of the elastic member 60 along the X-axis direction, increasing the reaction force of the elastic member 60 on the concave-cam assembly 50, and The friction force of each element along the surface perpendicular to the X-axis direction can be increased, thereby improving the stability when the first body 210 and the second body 220 are opened and closed.
  • the rotating shaft 100 provided in the present application adopts an integral structure and a hollow-shaped elastic member 60, which can be assembled to the central shaft 10 at one time, and the installation is simple, thereby improving the installation efficiency.
  • the elastic member 60 replaces the disc spring group 40a composed of multiple disc springs 41a, fundamentally avoiding the problems of low efficiency and high error rate caused by assembling multiple disc springs 41a, and no additional automatic assembly equipment is required.
  • the elastic member 60 with an integrated structure can avoid the use of multiple disc springs 41a in the related art or the spring has torsional force fluctuations perpendicular to the axial direction.
  • the structure of the elastic member 60 of the present application is more conducive to the first body 210 and the second Stability after opening between the two bodies 220 .
  • the elastic member 60 is always in the elastic deformation zone of the elastic member 60 during the process of being deformed by the extrusion force F, and no plastic deformation will occur, so the plastic deformation and elastic attenuation of the disc spring 41a in the related art will not occur. problem, increase the frequency of use. Furthermore, according to the structure of the elastic member 60 of the present application, when the extrusion force F experienced by the elastic member 60 exceeds a critical point t, the elastic member 60 has a constant force characteristic.

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Abstract

一种转轴（100）和包括转轴（100）的终端设备（200），转轴（100）包括中心轴（10）、第一支架（20）、第二支架（30）、弹性件（60）以及凹凸轮组件（50），第一支架（20）可旋转地设置于中心轴（10）上，第二支架（30）固定于中心轴（10）上，弹性件（60）设置于中心轴（10）上，弹性件（60）为镂空状且为一体结构，凹凸轮组件（50）设置于中心轴（10）上，凹凸轮组件（50）可使弹性件（60）产生形变；当第一支架（20）相较于第二支架（30）旋转时，凹凸轮组件（50）产生作用于弹性件（60）的挤压力使得镂空状的弹性件（60）产生形变，以使第一支架（20）与第二支架（30）之间呈一定的夹角。该转轴（100）的弹性件（60）为一体结构，便于安装，提高安装效率，镂空状的弹性件（60）使用频次高，且弹性件（60）具有恒力特性。

Description

转轴以及终端设备
相关申请的交叉引用
本申请要求在2021年10月09日提交中国专利局、申请号为202111176779.9、申请名称为“转轴以及终端设备”，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及机械结构技术领域，尤其涉及一种转轴以及终端设备。
背景技术
随着社会的发展，转轴的应用越来越广泛，例如笔记本电脑。现有的转轴安装复杂、安装误差大、使用寿命低；同时，具有上述转轴的终端设备在使用过程中，会产生扭力波动，影响用户体验。
发明内容
有鉴于此，有必要提供一种安装简单、扭力稳定、使用寿命长的转轴以及终端设备，以解决上述问题。
第一方面，本申请提供一种转轴，转轴包括中心轴、第一支架、第二支架、弹性件以及凹凸轮组件。第一支架可旋转地安装于中心轴上；第二支架固定连接于中心轴上；弹性件设置于中心轴上，弹性件为一体结构的中空筒体，筒体的筒壁开设有镂空孔；凹凸轮组件设置于中心轴上，凹凸轮组件可使弹性件产生形变；其中，当第一支架相较于第二支架旋转时，凹凸轮组件产生作用于弹性件的挤压力使得镂空状的弹性件产生形变，以使第一支架与第二支架之间呈一定的夹角。
上述设计中，采用一体结构且为镂空状的弹性件，可一次组装至中心轴上，安装简单，从而提升安装效率。弹性件代替由多个碟簧组成的碟簧组，从根本上避免组装多个碟簧所带来的效率低下、出错率高的问题，也无需设置额外的自动化组装设备。其次，一体结构的弹性件，可以避免相关技术中采用多块碟簧或者弹簧具有沿垂直于轴向方向的扭力波动，本申请的弹性件结构，更有利于第一本体与第二本体之间打开之后的稳定性。另外，弹性件在受到挤压力产生形变的过程中一直处于弹性件的弹性变形区，不会发生塑性形变，因此不会产生相关技术中的碟簧的塑性变形和弹性衰减的问题，提升使用频次。再者，还可以根据本申请弹性件的结构，设计弹性件所受到的挤压力超过一临界点时，弹性件具有恒力特性。
在一种可能的设计中，弹性件的筒壁开设有多个镂空孔及设置多条连接筋，多个镂空孔与多个连接筋交错连接以及间隔设置形成弹性件。
上述设计中，镂空孔的设置使得弹性件受到沿轴向方向的挤压力时，弹性件沿轴向方向能够产生形变，连接筋的延伸方向可以为任意方向，连接筋可以使得弹性件除轴向方向产生形变之外，还可以沿其他方向产生形变。
在一种可能的设计中，镂空孔的形状包括多边形以及弧形中的至少一种。
上述设计中，当镂空的形状为规则形状时，有利于根据弹性件所需要收到的挤压力进行设计和加工形成弹性件，并且弹性件沿中心轴的轴向方向的受力是均匀的。
在一种可能的设计中，多边形包括正方形、长方形、菱形、五边形、六边形中至少一种；弧形包括螺旋形、圆形、椭圆形以及半圆形中的至少一种。
上述设计中，镂空形状与转轴所需要受到的夹持力相关。
在一种可能的设计中，弹性件的材质选自金属、金属合金以及塑料中的一种。
上述设计中，金属或金属合金材质的弹性件的韧性更强，可使用的频次更高。塑料材质的弹性件可以采用注塑的方式形成弹性件，加工成本低。
在一种可能的设计中，中心轴包括固定连接的固定部、阻挡部以及杆部，阻挡部位于杆部与固定部之间；第二支架固定于固定部上，杆部依次穿设于第一支架、凹凸轮组件、弹性件，第一支架抵持于阻挡部上。
上述设计中，固定部用于固定第二本体；阻挡部用于与固定件相互配合，以使阻挡部与固定件之间的距离保持不变，在凹凸轮组件的总宽度发生变化时，挤压弹性件，使得弹性件产生形变；杆部用于将弹性件、凹凸轮组件连接成一整体。
在一种可能的设计中，第一支架包括第一固定板，第一固定板上开设有第一通孔，杆部穿过第一通孔，第一固定板抵持于阻挡部。
上述设计中，阻挡部限位第一固定板，以使第一支架与中心轴相对固定。
在一种可能的设计中，凹凸轮组件包括相邻接的凹轮与凸轮，凹轮与凸轮的其中一者与第一支架固定连接，凹轮与凸轮的另一者与中心轴固定连接。
上述设计中，由于第一支架与中心轴可旋转地连接，因此凹轮与凸轮活动连接，从而可以改变凹凸轮组件沿轴向方向的总宽度，以使弹性件产生形变。
在一种可能的设计中，第一固定板上设置有固定孔，凹轮包括相互连接的凹轮部与卡持部，凹轮部套设于杆部，卡持部卡持于固定孔中。
上述设计中，通过卡持部与固定孔相配合，以使凹轮与第一固定板固定连接。
在一种可能的设计中，凹轮部开设有第二通孔，第二通孔的最小直径大于杆部的最大直径。
上述设计中，杆部与凹轮能够相对旋转。
在一种可能的设计中，凸轮开设有第三通孔，第三通孔为扁平状，杆部为扁平状，凸轮套设于杆部。
上述设计中，中心轴旋转时，凸轮随中心轴同步旋转，设置扁平状的杆 部与扁平状的第三通孔，通过简单的结构设计，即可将凸轮与中心轴固定连接，并且还便于转轴的组装。
在一种可能的设计中，凹轮部与凸轮相连接的表面包括相连接的凹陷部与平磨区，凸轮与凹轮相连接的表面包括凸伸部，凸伸部可容置于凹陷部。
上述设计中，凹轮部的凹陷部与平磨区以及凸轮的凸伸部相适配，在凸轮与凹轮相对旋转，即可实现凹凸轮组件沿轴向方向的总宽度的变化，以使弹性件产生形变。
在一种可能的设计中，凸轮与凹轮相对旋转，凸伸部与平磨区接触之前，弹性件到达挤压力为一恒力的临界点。
上述设计中，即使位于平磨区的表面不平整，凸伸部与平磨区接触并相对旋转时，弹性件受到挤压力为恒力时，也会有同等大小的反作用力挤压凸轮与凹轮，以使凹轮与凸轮之间保持相对稳定，进而使得第一本体与第二本体保持用户所需要的开合角度。
在一种可能的设计中，转轴还包括固定件，固定件固定于杆部背离阻挡部的一侧并抵持于弹性件背离凹凸轮组件的表面。
上述设计中，固定件用于与阻挡部相互配合，以使固定件与阻挡部之间的距离保持不变，在凹凸轮组件的总宽度发生变化时，挤压弹性件，使得弹性件产生形变。
在一种可能的设计中，转轴还包括摩擦片，摩擦片包括第四通孔，第四通孔为扁平状，第四通孔的形状与杆部的形状相适配；摩擦片位于固定件与阻挡部之间。
上述设计中，可以减小固定件与凹凸轮组件之间的距离，进而减小弹性件沿轴向方向的宽度，增加弹性件作用于凹凸轮组件的反作用力，还可以增加各个元件沿垂直于轴向方向的摩擦力，从而提升第一本体与第二本体开合时的稳固性。
在一种可能的设计中，摩擦片位于凹轮与第一固定板之间。
上述设计中，摩擦片与凹轮和第一固定板相连接的表面均具有一定的粗糙度，由于凹轮与第一固定板之间固定连接，摩擦片与中心轴固定连接，摩擦片的设置，提升摩擦力，可以增加第一本体或第二本体具有沿重力方向的恢复阻力，从而提升第一本体与第二本体开合时的稳固性；还可以减小固定件与凹凸轮组件之间的距离，进而减小弹性件沿轴向方向的宽度，增加弹性件作用于凹凸轮组件的反作用力，还可以增加各个元件沿垂直于轴向方向的表面的摩擦力，从而进一步提升第一本体与第二本体开合时的稳固性。
第二方面，本申请提供一种终端设备，终端设备包括第一本体、第二本体以及转轴。第一本体与第一支架固定连接，第二本体与第二支架固定连接。
附图说明
图1为本申请实施例提供的终端设备的整体结构示意图。
图2为本申请一些实施例提供的包括碟簧组的转轴的整体结构示意图。
图3为图2所示的转轴的爆炸图。
图4为多个碟簧组装成图2所示的碟簧组的结构示意图。
图5为本申请另一些实施例提供的包括弹性件的转轴的整体结构示意图。
图6为图5所示的转轴的爆炸图。
图7为图6所示凹凸轮组件的爆炸图。
图8为图6所示的凹凸轮组件另一方位的爆炸图。
图9为转轴中的凹轮与凸轮未发生相对旋转时的整体结构示意图。
图10为转轴中的凹轮与凸轮发生相对旋转后的整体结构示意图。
图11为转轴的镂空形状为六边形的整体结构示意图。
图12为转轴的镂空形状为四边形的平面示意图。
图13为转轴的镂空形状为螺旋形的整体结构示意图。
图14为转轴的镂空形状为圆形的平面示意图。
图15为转轴的镂空形状为六边形时产生形变前(实线)和产生形变后(虚线)的结构示意图。
图16为转轴受到的挤压力与轴向方向形变量的变化关系示意图。
主要元件符号说明
终端设备 200
第一本体 210
第二本体 220
转轴 100、100a
中心轴 10、10a
固定部 11
第一穿孔 112
阻挡部 13
杆部 15
第一支架 20、20a
第一固定板 21
第一通孔 212
固定孔 214
第二固定板 23
第二穿孔 232
第二支架 30、30a
碟簧组 40a
碟簧 41a
凹凸轮组件 50、50a
凹轮 51
凹轮部 512
第二通孔 5122
凹陷部 5124
平磨区 5126
卡持部 514
凸轮 53
第三通孔 532
凸伸部 534
弹性件 60、60a、60b、60c
第五通孔 61
镂空孔 63、63a、63b、63c
连接筋 65、65a、65b、65c
固定件 70
摩擦片 80
第四通孔 81
距离 D
宽度 W1、W2
临界点 t
角度 θ
挤压力 F
具体实施方式
为了能够更清楚地理解本申请的上述目的、特征和优点，下面结合附图和具体实施方式对本申请进行详细描述。需要说明的是，在不冲突的情况下，本申请的实施方式及实施方式中的特征可以相互组合。在下面的描述中阐述了很多具体细节以便于充分理解本申请，所描述的实施方式仅仅是本申请一部分实施方式，而不是全部的实施方式。
除非另有定义，本文所使用的所有的技术和科学术语与属于本申请的技术领域的技术人员通常理解的含义相同。本文中在本申请的说明书中所使用的术语只是为了描述具体的实施方式的目的，不是旨在于限制本申请。本文所使用的术语“和/或”包括一个或多个相关的所列项目的所有的和任意的组合。
在本申请的各实施例中，为了便于描述而非限制本申请，本申请专利申请说明书以及权利要求书中使用的术语“连接”并非限定于物理的或者机械的连接，不管是直接的还是间接的。“上”、“下”、“上方”、“下方”、“左”、“右”等仅用于表示相对位置关系，当被描述对象的绝对位置改变后，则该相对位置关系也相应地改变。
请参阅图1，本申请实施例提供一种终端设备200，终端设备200包括但 不限于电脑、手机、门、蓝牙耳机盒、眼镜盒等需要使用到转轴100的产品。在本实施例中，终端设备200为一笔记本电脑。
终端设备200包括第一本体210、第二本体220以及转轴100，转轴100连接第一本体210与第二本体220，通过转轴100的作用可以改变第一本体210与第二本体220的开合角度，并保持在用户所需要的开合角度。
第一本体210与第二本体220的具体名称与转轴100的使用场景有关。例如，当终端设备200为笔记本电脑时，第一本体210可以是键盘，第二本体220可以是显示屏；当终端设备200为门时，第一本体210可以是门框，第二本体220可以是门板。上述仅为举例说明，并不以此为限制。
请参阅图2，本申请一些实施例提供一种转轴100a，转轴100a包括中心轴10a、第一支架20a、第二支架30a、碟簧组40a以及凹凸轮组件50a。第一支架20a可旋转地设置于中心轴10a上，第二支架30a固定于中心轴10a上，碟簧组40a设置于中心轴10a上，凹凸轮组件50a设置于中心轴10a上，凹凸轮组件50a可使碟簧组40a沿中心轴10a的延伸方向产生形变。第一支架20a用于与第一本体210固定，第二支架30a用于与第二本体220固定。第一支架20a与第二支架30a可旋转地连接，从而使得第一本体210与第二本体220能够开合。
请一并参阅图3和图4，碟簧组40a由多块碟簧41a组装形成，每一碟簧41a为一圆环拱形薄片，碟簧41a的厚度可以为0.4mm-0.6mm。在本实施例中，碟簧组40a由五块碟簧41a组装形成。其中，碟簧41a在组装形成碟簧组40a的过程中具有正反之分，在组装过程中，需要人工正反依次交替组装，从而形成具有弹性的碟簧组40a。
本申请发明人发现，人工组装效率低下且容易出错，在一些使用场景中，例如碟簧41a的尺寸较小、碟簧41a的正反较难区分或者需要使用的碟簧41a的数量较多等，更加增加了人工出错的概率；通过自动化组装代替人工组装，则需要额外的自动化组装设备，提高了生产成本；其次，具有转轴100a的终端设备200通常是多次使用，因此，转轴100a的使用频次较高，上述碟簧组40a通常能使用的次数有限(例如2万-3万次)，便会出现较大的弹力衰减，进而造成转轴100a扭矩的急剧下降，影响用户使用；另外，由于碟簧组40a是由多块碟簧41a组成，当第一本体210与第二本体220之间具有一定的夹角时，由于第一本体210或者第二本体220的重力存在，引起第一本体210或第二本体220具有沿重力方向的恢复趋势，多块碟簧41a之间具有沿垂直于轴向方向的扭力波动，使得第一本体210与第二本体220之间打开之后的角度较难保持，本申请发明人还发现，采用弹簧代替上述碟簧组40a时，也会存在这一问题，采用弹簧代替上述碟簧组40a时，弹簧的弹性难以支撑相互打开之后的第一本体210或第二本体220。再者，碟簧组40a或者弹簧受到的外力作用与形变量呈正相关，即外力大小发生变化时，碟簧组40a或者弹簧形变量会发生变化，导致作用于第一本体210或第二本体220的作用力不稳定。
请参阅图5，本申请另一些实施例提供一种转轴100，转轴100包括中心轴10、第一支架20、第二支架30、弹性件60以及凹凸轮组件50。第一支架20与中心轴10可相对旋转地连接，第二支架30与中心轴10固定连接，弹性件60设置于中心轴10上，弹性件60为镂空状，凹凸轮组件50设置于中心轴10上，凹凸轮组件50可使弹性件60产生形变。其中，当第一支架20相较于第二支架30旋转时，凹凸轮组件50使得镂空状的弹性件60产生形变，以使第一支架20与第二支架30之间呈一定的夹角。
具体地，请一并参阅图6，中心轴10包括固定连接的固定部11、阻挡部13以及杆部15，阻挡部13位于固定部11与杆部15之间，杆部15在阻挡部13背离固定部11的一侧向外延伸，为便于说明，定义杆部15延伸的方向为X轴方向(即杆部15的轴向方向)。沿垂直于X轴方向，阻挡部13的直径大于杆部15的直径。
固定部11为一扁平状的块状，固定部11上开设有第一穿孔112，第一穿孔112可以与螺母相配合，用于固定第二本体220。
杆部15依次穿设于第一支架20、凹凸轮组件50以及弹性件60，第一支架20抵持于阻挡部13，凹凸轮组件50位于弹性件60与第一支架20之间，转轴100还包括固定件70，固定件70位于杆部15的端部从而将第一支架20、弹性件60以及凹凸轮组件50固定于杆部15上，以使固定件70与第一支架20沿X轴方向的距离D固定。在本实施例中，固定件70为一螺母，在其他实施方式中，固定方式并不仅限于采用螺母固定，还可以是粘结或者卡接等。
第一支架20包括第一固定板21与第二固定板23，第一固定板21与第二固定板23固定连接。第二固定板23设置于第一固定板21的一表面并与第一固定板21之间具有一定的夹角。在本实施例中，第二固定板23与第一固定板21之间相互垂直。在其他实施例中，第二固定板23与第一固定板21之间的角度并不限制，可以根据需要进行设置。
第二固定板23上设置有第二穿孔232，第二穿孔232可以与螺母相配合，用于固定第一本体210。
第一固定板21上设置有第一通孔212以及固定孔214。第一通孔212贯穿第一固定板21的相对两表面，第一通孔212用于中心轴10穿过，第一固定板21抵持于阻挡部13背离固定部11的表面。固定孔214可以是通孔，也可以是容置槽，在本实施例中，固定孔214是通孔，用于限位凹凸轮组件50。
凹凸轮组件50套设于杆部15。凹凸轮组件50包括相邻接的凹轮51与凸轮53，凹轮51与凸轮53相连接的表面相互配合，凹轮51与凸轮53可活动地连接。凹轮51与凸轮53的其中一者与第一支架20固定连接，凹轮51与凸轮53的另一者与中心轴10固定连接，当凹轮51与凸轮53产生相对运动时，凹轮51与凸轮53沿X轴方向的总宽度发生变化，从而有一相对的挤压力F作用于弹性件60上，使得弹性件60产生形变。
具体地，请一并参阅图7和图8，在本实施例中，凹轮51与第一固定板21固定连接，凸轮53与杆部15固定连接。凹轮51包括凹轮部512与卡持 部514，卡持部514与凹轮部512的边缘区域连接并朝向第一固定板21的方向延伸，卡持部514的至少部分卡持于固定孔214中，以使凹轮51与第一支架20固定连接。凹轮部512开设有第二通孔5122，第二通孔5122的最小直径大于杆部15的最大直径，以使杆部15与凹轮51能够相对旋转。凸轮53开设有第三通孔532，第三通孔532为扁平状，杆部15也呈扁平状，第三通孔532与杆部15相适配，凸轮53与杆部15相对固定，中心轴10旋转时，凸轮53随中心轴10同步旋转，设置扁平状的杆部15与扁平状的第三通孔532，通过简单的结构设计，即可将凸轮53与中心轴10固定连接，并且还便于转轴100的组装。在其他实施例中，凸轮53与中心轴10的固定方式还可以是粘结、卡接等。
凹轮部512与凸轮53相连接的表面包括相连接的凹陷部5124与平磨区5126，凸轮53与凹轮51相连接的表面包括凸伸部534。当凹轮51与凸轮53未发生相对旋转时，凸伸部534与凹陷部5124相对应，即凸伸部534容置于凹陷部5124中。在本实施例中，凹陷部5124与凸伸部534的数量均为两个，两个凹陷部5124与两个凸伸部534分别对应设置，平磨区5126的数量也为两个，凹陷部5124与平磨区5126间隔设置，凹陷部5124或凸伸部534的数量与第一本体210与第二本体220相互打开之后所要保持的角度有关。在其他实施例中，凹陷部5124与凸伸部534的数量并不限制。
请参阅图9，凹轮51与凸轮53未发生相对旋转时，凹轮51与凸轮53具有一沿X轴方向的总宽度W1。固定凹轮51，旋转凸轮53，则凸伸部534沿着凹陷部5124的侧壁与凹轮51逐渐产生相对旋转，随着相对旋转的角度的增大，凸轮53与凹轮51沿X轴方向的总宽度W1逐渐变大，由于固定件70与第一固定板21之间的距离D一定，因此弹性件60的宽度逐渐减小，弹性件60所受到的挤压力F逐渐增大；请参阅图10，当凸伸部534旋转至凹陷部5124与平磨区5126的连接点时，凸轮53与凹轮51的总宽度W2达到最大，弹性件60所受到的挤压力F达到最大；继续增加凸轮53与凹轮51之间的相对旋转，凸轮53与凹轮51的总宽度W2不会发生改变，此时，弹性件60所受到的作用力也不会再发生改变。理论上，平磨区5126应为平面，然而在实际加工平面的限制，无法达到绝对平整，因此，在实际的产品中，凸伸部534与平磨区5126接触并相对旋转时，由于平磨区5126的不平整，会产生微小的波动，则导致弹性件60的形变量也会产生一定的波动。
可以理解，凹轮51与第一支架20固定连接，第一支架20与第一本体210固定连接，凸轮53与中心轴10固定连接，中心轴10与第二本体220固定连接，则凹轮51与凸轮53产生相对旋转，同步带动第一本体210与第二本体220产生相对旋转，第一本体210与第二本体220之间相对旋转的角度可以根据需要进行设置。
形成凹陷部5124与凸伸部534的表面均为弧面，凹轮51与凸轮53发生相对旋转运动时，有利于作用于弹性件60的挤压力F平滑过渡，提升用户体验。
请参阅图11至图14，弹性件60为一镂空的筒体，弹性件60为一体结构。弹性件60的中心具有第五通孔61，用于套设于杆部15上。一体结构的弹性件60，可一次组装至中心轴10上，安装简单，从而提升安装效率。弹性件60代替由多个碟簧41a组成的碟簧组40a，从根本上避免组装多个碟簧41a所带来的效率低下、出错率高的问题，也无需设置额外的自动化组装设备。
镂空的形状可以是规则形状或者不规则的形状，规则的形状包括但不限于多边形(请参阅图11和图12)或者弧形(请参阅图13和图14)等，其中，多边形包括但不限于正方形、长方形、菱形、五边形、六边形等，弧形包括但不限于螺旋形、圆形、椭圆形或者半圆形等，在同一实施例中，上述形状可以相互组合。当镂空的形状为规则形状时，有利于根据弹性件60所需要收到的挤压力F进行设计和加工形成弹性件60，并且弹性件60沿X轴方向的受力是均匀的。
具体的，请参阅图11，本申请实施例中提供的一镂空的弹性件60的筒壁开设多个镂空孔63及设置多条连接筋65，镂空孔63与第五通孔61连通，镂空孔63的形状为六边形，多个镂空孔63与多个连接筋65交错连接以及间隔设置形成镂空的弹性件60，从而使弹性件60的筒壁形成类似蜂窝状的镂空筒壁。
请参阅图12，本申请实施例中提供的另一镂空的弹性件60a的筒壁开设多个镂空孔63a及设置多条连接筋65a，镂空孔63a与第五通孔(图未示)连通，镂空孔63a为菱形，多个镂空孔63a与多个连接筋65a交错连接以及间隔设置形成镂空的弹性件60a。
请参阅图13，本申请实施例中提供的另一镂空的弹性件60b的筒壁开设多个镂空孔63b、位于镂空孔63b之间的多条连接筋65b，镂空孔63b与第五通孔61连通，镂空孔63b为螺旋形，多个镂空孔63b与多个连接筋65b交错连接以及间隔设置形成镂空的弹性件60b。其中，连接筋65b的延伸方向包括沿X轴方向(轴向方向)延伸以及与X轴方向相交方向延伸，其中，沿X轴方向延伸的连接筋65b使得弹性件60b在受到挤压力F时，具有沿与X轴方向相交方向产生形变的可能性。
请参阅图14，本申请实施例中提供的另一镂空的弹性件60c的筒壁开设多个镂空孔63c及设置多条连接筋65c，镂空孔63c与第五通孔(图未示)连通，镂空孔63c为圆形，多个镂空孔63c与多个连接筋65c交错连接以及间隔设置形成镂空的弹性件60c。
根据连接筋65位置的不同，形成的镂空形状不同，连接筋65的延伸方向可以为任意方向，连接筋65可以使得弹性件60除轴向方向产生形变之外，还可以沿其他方向产生形变。当凹凸轮组件50沿X轴方向的总宽度产生变化时，弹性件60受到挤压力F，由于弹性件60为镂空状，请参阅图15，以镂空形状为六边形为例(如图15中的实线)，围设形成六边形的连接筋65与挤压力F垂直，请一并参阅图16，弹性件60受到挤压力F时，可以沿着 X轴方向被压缩从而产生形变，随着挤压力F的增加，弹性件60的形变量增加；当弹性件60受到的挤压力F达到一临界点t(如图16中的t点)时，弹性件60还可以沿着与X轴相交的方向向外鼓起产生形变(如图15中的虚线)，弹性件60的连接筋65可以沿多个方向产生形变(并不仅限于沿X轴方向产生形变)，即，凹凸轮组件50继续挤压弹性件60，超过临界点t，弹性件60的形变量包括沿X轴方向的形变以及与X轴相交方向的形变，根据屈曲分析原理，弹性件60所受到的挤压力F不变，此时，转轴100的扭力稳定。
在一些实施方式中，达到临界点t(即弹性件60受到的挤压力F变成恒力)在凸伸部534旋转至凹陷部5124与平磨区5126的连接点之前达到，如此，即使位于平磨区5126的表面不平整，凸伸部534与平磨区5126接触并相对旋转时，弹性件60受到挤压力F为恒力时，也会有同等大小的反作用力挤压凸轮53与凹轮51，以使凹轮51与凸轮53之间保持相对稳定，进而使得第一本体210与第二本体220保持用户所需要的开合角度。其中，弹性件60的临界点t与镂空形状、弹性件60的材质、厚度、连接筋65与挤压力F之间的角度θ(请参阅图15)等均有一定的关系，可以根据弹性件60所需要的挤压力F综合计算弹性件60所选择的材料、壁厚、镂空形状等，使得弹性件60能够产生合适的挤压力F，也可以根据弹性件60是否需要达到恒力区间设计弹性件60的材质、壁厚、镂空形状等，当转轴100应用到具体的终端设备200中时，以实现转轴100的功能。另外，弹性件60在受到挤压力F产生形变的过程中一直处于弹性件60的弹性变形区，不会发生塑性形变，因此不会产生相关技术中碟簧41a的塑性变形和弹性衰减的问题。
恒力区间的范围(即图16中沿轴向方向形变量方向挤压力F为恒力时的宽度)与连接筋65和挤压力F之间的角度θ也有一定的关系，在一些实施方式中，当弹性件60的壁厚、材料等条件相同时，角度θ的范围为50°-70°时，恒力区间的范围最大；角度θ小于50°时，恒力区间的范围随角度θ的增加而增加；角度θ大于70°时，恒力区间的范围随角度θ的增加而减小。可以根据转轴实际应用需要选择连接筋65与挤压力F之间的角度θ，即根据需要选择镂空形状以及镂空形状的排列方向。
弹性件60的材质可以是金属、金属合金或者塑料。金属或金属合金材质的弹性件60的韧性更强，可使用的频次更高。塑料材质的弹性件60可以采用注塑的方式形成弹性件60，加工成本低。在一些实施方式中，弹性件60的使用频次超过十万次。
转轴100还包括摩擦片80，摩擦片80的表面粗糙度较大。摩擦片80包括第四通孔81，第四通孔81为扁平状，第四通孔81的形状与杆部15的形状相适配，摩擦片80与杆部15固定连接。摩擦片80位于凹轮51与第一固定板21之间，摩擦片80与凹轮51和第一固定板21相连接的表面均具有一定的粗糙度，由于凹轮51与第一固定板21之间固定连接，摩擦片80与中心轴10固定连接，摩擦片80的设置，可以增加摩擦片80与相邻元件(即凹轮51与第一固定板21)之间的摩擦力，当第一本体210与第二本体220之间具 有夹角时，由于第一本体210或者第二本体220的重力存在，引起第一本体210或第二本体220具有沿重力方向的恢复趋势，提升摩擦力，可以增加第一本体210或第二本体220具有沿重力方向的恢复阻力，从而提升第一本体210与第二本体220开合时的稳固性。进一步地，摩擦片80的设置，可以减小固定件70与凹凸轮组件50之间的距离，进而减小弹性件60沿X轴方向的宽度，增加弹性件60作用于凹凸轮组件50的反作用力，还可以增加各个元件沿垂直于X轴方向的表面的摩擦力，从而进一步提升第一本体210与第二本体220开合时的稳固性。
凹轮51和第一固定板21与摩擦片80相邻接的表面也可以设置与摩擦片80的表面粗糙度相适配的凹槽或凸起，以使转轴100在转动过程中以及第一本体210或第二本体220维持一定的夹角时，具有合适的摩擦力。
摩擦片80也可以位于凸轮53与固定件70之间，例如位于固定件70与弹性件60之间或者弹性件60与凹凸轮组件50之间。摩擦片80的设置，可以减小固定件70与凹凸轮组件50之间的距离，进而减小弹性件60沿X轴方向的宽度，增加弹性件60作用于凹凸轮组件50的反作用力，还可以增加各个元件沿垂直于X轴方向的表面的摩擦力，从而提升第一本体210与第二本体220开合时的稳固性。
本申请提供的转轴100，采用一体结构且为镂空状的弹性件60，可一次组装至中心轴10上，安装简单，从而提升安装效率。弹性件60代替由多个碟簧41a组成的碟簧组40a，从根本上避免组装多个碟簧41a所带来的效率低下、出错率高的问题，也无需设置额外的自动化组装设备。其次，一体结构的弹性件60，可以避免相关技术中采用多块碟簧41a或者弹簧具有沿垂直于轴向方向的扭力波动，本申请的弹性件60结构，更有利于第一本体210与第二本体220之间打开之后的稳定性。另外，弹性件60在受到挤压力F产生形变的过程中一直处于弹性件60的弹性变形区，不会发生塑性形变，因此不会产生相关技术中的碟簧41a的塑性变形和弹性衰减的问题，提升使用频次。再者，还可以根据本申请弹性件60的结构，设计弹性件60所受到的挤压力F超过一临界点t时，弹性件60具有恒力特性。
以上实施方式仅用以说明本申请的技术方案而非限制，尽管参照以上较佳实施方式对本申请进行了详细说明，本领域的普通技术人员应当理解，可以对本申请的技术方案进行修改或等同替换都不应脱离本申请技术方案的精神和范围。

Claims (32)

  1. 一种转轴，其特征在于，包括：
    中心轴；
    第一支架，可旋转地安装于所述中心轴上；
    第二支架，固定连接于所述中心轴上；
    弹性件，设置于所述中心轴上，所述弹性件为一体结构的中空筒体，所述筒体的筒壁开设有镂空孔；以及
    凹凸轮组件，设置于所述中心轴上，所述凹凸轮组件可使所述弹性件产生形变；
    其中，当所述第一支架相较于所述第二支架旋转时，所述凹凸轮组件产生作用于所述弹性件的挤压力使得镂空状的所述弹性件产生形变，以使所述第一支架与所述第二支架之间呈一定的夹角。
  2. 根据权利要求1所述的转轴，其特征在于，所述弹性件的筒壁开设有多个所述镂空孔及设置多条连接筋，多个所述镂空孔与多个所述连接筋交错连接以及间隔设置形成所述弹性件。
  3. 根据权利要求1所述的转轴，其特征在于，所述镂空孔的形状包括多边形以及弧形中的至少一种。
  4. 根据权利要求3所述的转轴，其特征在于，所述多边形包括正方形、长方形、菱形、五边形、六边形中至少一种；所述弧形包括螺旋形、圆形、椭圆形以及半圆形中的至少一种。
  5. 根据权利要求1所述的转轴，其特征在于，所述弹性件的材质选自金属、金属合金以及塑料中的一种。
  6. 根据权利要求1-5任意一项所述的转轴，其特征在于，所述中心轴包括固定连接的固定部、阻挡部以及杆部，所述阻挡部位于所述杆部与所述固定部之间；所述第二支架固定于所述固定部上，所述杆部依次穿设于所述第一支架、所述凹凸轮组件、所述弹性件，所述第一支架抵持于所述阻挡部上。
  7. 根据权利要求6所述的转轴，其特征在于，所述第一支架包括第一固定板，所述第一固定板上开设有第一通孔，所述杆部穿过所述第一通孔，所述第一固定板抵持于所述阻挡部。
  8. 根据权利要求7所述的转轴，其特征在于，所述凹凸轮组件包括相邻接的凹轮与凸轮，所述凹轮与所述凸轮的其中一者与所述第一支架固定连接，所述凹轮与所述凸轮的另一者与所述中心轴固定连接。
  9. 根据权利要求8所述的转轴，其特征在于，所述第一固定板上设置有固定孔，所述凹轮包括相互连接的凹轮部与卡持部，所述凹轮部套设于所述杆部，所述卡持部卡持于所述固定孔中。
  10. 根据权利要求9所述的转轴，其特征在于，所述凹轮部开设有第二通孔，所述第二通孔的最小直径大于所述杆部的最大直径。
  11. 根据权利要求9所述的转轴，其特征在于，所述凸轮开设有第三通孔，所述第三通孔为扁平状，所述杆部为扁平状，所述凸轮套设于所述杆部。
  12. 根据权利要求9所述的转轴，其特征在于，所述凹轮部与所述凸轮相连接的表面包括相连接的凹陷部与平磨区，所述凸轮与所述凹轮相连接的表面包括凸伸部，所述凸伸部可容置于所述凹陷部。
  13. 根据权利要求12所述的转轴，其特征在于，所述凸轮与所述凹轮相对旋转，所述凸伸部与所述平磨区接触之前，所述弹性件到达所述挤压力为一恒力的临界点。
  14. 根据权利要求8所述的转轴，其特征在于，所述转轴还包括固定件，所述固定件固定于所述杆部背离所述阻挡部的一侧并抵持于所述弹性件背离所述凹凸轮组件的表面。
  15. 根据权利要求14所述的转轴，其特征在于，所述转轴还包括摩擦片，所述摩擦片包括第四通孔，所述第四通孔为扁平状，所述第四通孔的形状与所述杆部的形状相适配；所述摩擦片位于所述固定件与所述阻挡部之间。
  16. 根据权利要求15所述的转轴，其特征在于，所述摩擦片位于所述凹轮与所述第一固定板之间。
  17. 一种终端设备，其特征在于，所述终端设备包括第一本体、第二本体以及权利要求1-16任意一项所述的转轴；所述第一本体与所述第一支架固定连接，所述第二本体与所述第二支架固定连接。
  18. 一种转轴，其特征在于，包括：
    中心轴；
    第一支架，可旋转地安装于所述中心轴上；
    第二支架，固定连接于所述中心轴上；
    弹性件，设置于所述中心轴上，所述弹性件为一体结构的中空筒体，所述筒体的筒壁开设有镂空孔；以及
    凹凸轮组件，设置于所述中心轴上，所述凹凸轮组件包括相邻接的凹轮与凸轮，所述凹轮与所述凸轮相连接的表面包括相连接的凹陷部与平磨区，所述凸轮与所述凹轮相连接的表面包括凸伸部，所述凸伸部可容置于所述凹陷部，所述凸轮与所述凹轮相对旋转可使所述弹性件产生形变；
    其中，当所述第一支架相较于所述第二支架旋转时，所述凹凸轮组件产生作用于所述弹性件的挤压力使得镂空状的所述弹性件产生形变，以使所述第一支架与所述第二支架之间呈一定的夹角，所述凸伸部与所述平磨区接触之前，所述弹性件到达所述挤压力为一恒力的临界点。
  19. 根据权利要求18所述的转轴，其特征在于，所述弹性件的筒壁开设有多个所述镂空孔及设置多条连接筋，多个所述镂空孔与多个所述连接筋交错连接以及间隔设置形成所述弹性件。
  20. 根据权利要求18所述的转轴，其特征在于，所述镂空孔的形状包括多边形以及弧形中的至少一种。
  21. 根据权利要求20所述的转轴，其特征在于，所述多边形包括正方形、长方形、菱形、五边形、六边形中至少一种；所述弧形包括螺旋形、圆形、椭圆形以及半圆形中的至少一种。
  22. 根据权利要求18所述的转轴，其特征在于，所述弹性件的材质选自金属、金属合金以及塑料中的一种。
  23. 根据权利要求18-22任意一项所述的转轴，其特征在于，所述中心轴包括固定连接的固定部、阻挡部以及杆部，所述阻挡部位于所述杆部与所述固定部之间；所述第二支架固定于所述固定部上，所述杆部依次穿设于所述第一支架、所述凹凸轮组件、所述弹性件，所述第一支架抵持于所述阻挡部上。
  24. 根据权利要求23所述的转轴，其特征在于，所述第一支架包括第一固定板，所述第一固定板上开设有第一通孔，所述杆部穿过所述第一通孔，所述第一固定板抵持于所述阻挡部。
  25. 根据权利要求24所述的转轴，其特征在于，所述凹轮与所述凸轮的其中一者与所述第一支架固定连接，所述凹轮与所述凸轮的另一者与所述中心轴固定连接。
  26. 根据权利要求25所述的转轴，其特征在于，所述第一固定板上设置有固定孔，所述凹轮包括相互连接的凹轮部与卡持部，所述凹轮部包括所述凹陷部与所述平磨区，所述凹轮部套设于所述杆部，所述卡持部卡持于所述固定孔中。
  27. 根据权利要求26所述的转轴，其特征在于，所述凹轮部开设有第二通孔，所述第二通孔的最小直径大于所述杆部的最大直径。
  28. 根据权利要求26所述的转轴，其特征在于，所述凸轮开设有第三通孔，所述第三通孔为扁平状，所述杆部为扁平状，所述凸轮套设于所述杆部。
  29. 根据权利要求25所述的转轴，其特征在于，所述转轴还包括固定件，所述固定件固定于所述杆部背离所述阻挡部的一侧并抵持于所述弹性件背离所述凹凸轮组件的表面。
  30. 根据权利要求29所述的转轴，其特征在于，所述转轴还包括摩擦片，所述摩擦片包括第四通孔，所述第四通孔为扁平状，所述第四通孔的形状与所述杆部的形状相适配；所述摩擦片位于所述固定件与所述阻挡部之间。
  31. 根据权利要求30所述的转轴，其特征在于，所述摩擦片位于所述凹轮与所述第一固定板之间。
  32. 一种终端设备，其特征在于，所述终端设备包括第一本体、第二本体以及权利要求18-31任意一项所述的转轴；所述第一本体与所述第一支架固定连接，所述第二本体与所述第二支架固定连接。
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