WO2012105296A1 - Hinge device - Google Patents

Hinge device Download PDF

Info

Publication number
WO2012105296A1
WO2012105296A1 PCT/JP2012/050641 JP2012050641W WO2012105296A1 WO 2012105296 A1 WO2012105296 A1 WO 2012105296A1 JP 2012050641 W JP2012050641 W JP 2012050641W WO 2012105296 A1 WO2012105296 A1 WO 2012105296A1
Authority
WO
WIPO (PCT)
Prior art keywords
friction
cam member
shaft
cam
friction member
Prior art date
Application number
PCT/JP2012/050641
Other languages
French (fr)
Japanese (ja)
Inventor
貴雄 小林
斎藤　誠
森本　隆
Original Assignee
日本発條株式会社
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 日本発條株式会社 filed Critical 日本発條株式会社
Priority to CN2012800076141A priority Critical patent/CN103339392A/en
Priority to JP2012555775A priority patent/JP5598776B2/en
Publication of WO2012105296A1 publication Critical patent/WO2012105296A1/en

Links

Images

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

Definitions

  • the present invention relates to a hinge device incorporated in a notebook computer, a mobile phone, or the like, for example, a hinge device that pivotally connects a lid to the main body so as to open and close the lid with respect to the main body.
  • FIG. 13 shows an example of a notebook personal computer 100.
  • the main body keyboard
  • the lid is a second member 120
  • the second member 120 can be opened and closed to the first member 110. It is attached.
  • the opening and closing of the second member 120 is performed by rotating the first member 110, and the second member 120 is pivotally connected to the first member 110. Therefore, the members 110 and 120 are hinged. They are connected by a device 130.
  • FIG. 14 is a diagram for explaining the characteristics required for the notebook personal computer 100 described above.
  • the second member 120 formed of a display is held at an arbitrary angle within a predetermined angle (20 to 180 °) range. A free stop function is required. Also, in the vicinity of full closure (0 to 20 °), a suction operation is required in which the second member 120 is closed by itself.
  • FIG. 15 shows a conventional hinge device 200 described in Patent Document 1, and a suction operation is possible.
  • FIG. 15 illustrates a state where the second member 120 is closed with respect to the first member 110 at an angle of 0 °.
  • a friction member 210 including a bracket is fixed to the first member 110 in a rising shape, and a cam member 220 is attached to the second member 120.
  • the friction member 210 and the cam member 220 are in surface contact with each other.
  • a shaft member 230 is attached to the second member 120 with a screw 240, and a shaft portion 231 of the shaft member 230 passes through the friction member 210 and the cam member 220. Further, a friction torque is generated by the friction plate 250 being sandwiched between the friction member 210 and the shaft member 230.
  • the biasing means 270 formed by overlapping a plurality of disc springs is attached to the shaft portion 231 of the shaft member 230.
  • the biasing means 270 made of a disc spring biases the cam member 220 so as to press it against the friction member 210.
  • a washer 280 through which the shaft part 231 of the shaft member 230 passes is provided outside the biasing means 270, and the biasing means 270 is tightened by crimping the tip end portion of the shaft part 231 of the shaft member 230 that has come out of the washer 280. Let it be bent. As a result, the biasing means 270 biases the cam member 220.
  • the shaft portion 231 of the shaft member 230 has a non-circular outer shape such as a parallel cut, a D cut, or a rectangle, while the shaft hole of the friction member 210 through which the shaft portion 231 passes is circular.
  • the shaft member 230 rotates, but the friction member 210 does not rotate.
  • the shaft hole of the cam member 220 is a non-circular shape corresponding to the shaft hole 231 of the shaft member 230, and the shaft portion 231 of the shaft member 230 passes through this shaft hole, so that the cam member 220 has a shaft hole. It rotates together with the member 230 (that is, the second member 120).
  • the cam member 220 rotates with respect to the friction member 210 and the opposing surface in contact with the friction member 210 becomes a friction surface to generate a frictional force.
  • the rotation of 220 stops, and the second member 120 is held at an arbitrary angle.
  • a convex portion 291 is formed on the surface (friction surface) of the cam member 220 facing the friction member 210
  • a concave portion 292 is formed on the surface (friction surface) of the friction member 210.
  • These convex portions 291 and concave portions 292 formed on the friction surface correspond to an opening angle of the second member 120 from around 20 °, and are formed so as to be fitted when the opening angle is 0 °.
  • slope portions are formed at the start and end portions of the convex portion 291 and the concave portion 292. When the convex portion 291 and the concave portion 292 reach a fitting position, they slide between the slope portions. It has come to produce.
  • the cam member 220 When the slope portion of the convex portion 291 and the slope portion of the concave portion 292 come into contact with each other by the closing operation of the second member 120, the cam member 220 performs a suction operation due to the rotational torque caused by the slip generated between them and the own weight of the second member 120. Thus, the second member 120 can be closed by itself.
  • Patent Documents 2 to 6 describe structures that increase the friction torque and secure the suction operation.
  • many friction surfaces are provided to reduce the surface pressure per surface.
  • the convex portions and the concave portions are increased in order to ensure the suction operation.
  • FIG. 16 shows a hinge device 300 having such a structure.
  • 16 has a structure in which the second friction member 310 is assembled to the friction member 210 in a fixed state, and the cam member 220 is sandwiched between the friction member 210 and the second friction member 310. Further, a second cam member 320 that is in surface contact with the second friction member 310 is disposed outside the second friction member 310 (on the biasing means 270 side).
  • the second cam member 320 is provided with a convex portion 291 on the surface facing the second friction member 310, the second friction member 310 is provided with a concave portion 292 on the surface facing the second cam member 320,
  • the cam member 220 is provided with a convex portion 291 on the surface facing the friction member 210, and the friction member 210 is provided with a concave portion 292 on the surface facing the cam member 220 to perform the suction operation.
  • FIG. 16A shows a state in which the opening angle of the second member 120 is 0 °. In this state, the convex portion 291 and the concave portion 292 are fitted.
  • FIG. 16B shows a state in which the opening angle of the second member 120 is 90 °, and the convex portion 291 and the concave portion 292 are not fitted.
  • the opposing surface of the flat second friction member 310 and the cam member 220 facing each other in a plane, the opposing surface of the cam member 220 and the friction member 210 facing each other formed with the uneven portions 201 and 292, and the uneven portion 291. , 292 are not formed, and four surfaces of the facing surfaces of the friction member 210 and the friction plate 250 facing each other in a plane are used as friction surfaces.
  • the convex portion 291 is provided in each of the second cam member 320 and the cam member 220, and the concave portion 292 is provided in each of the second friction member 310 and the friction member 210. Since they are arranged in series, there is a problem that they become longer in the axial direction. Further, since the second cam member 320 and the second friction member 310 are required, the number of parts is large and the structure is complicated.
  • the stroke during the suction operation is long, the stroke of the spring constituting the urging means is also large. Therefore, it is necessary to increase the number of springs in order to ensure durability. That is, when the height of the convex portion 291 is H, the entire hinge device 300 has a stroke of 2H, and the number of springs is twice that of the hinge device 200 of FIG. 15 to accommodate this stroke. . As the number of springs increases in this way, the structure becomes more complicated.
  • the present invention has been made in consideration of such conventional problems, and the number of parts can be reduced without being elongated in the axial direction, and the friction torque can be reduced despite the simple structure. It is an object of the present invention to provide a hinge device that can be stabilized and can secure a suction operation.
  • a hinge device is a hinge device that connects a first member and a second member so as to be relatively rotatable, and includes a first friction member fixed to one member, and the first friction member rotatably.
  • a shaft member that is supported and to which the other member is fixed, a cam member that is rotationally restrained by the shaft member and that can be moved in the axial direction, and is fixed in a state of being opposed to the first friction member with the cam member interposed therebetween.
  • a convex portion or a concave portion that fits into the convex portion or the concave portion of the cam member is formed on the friction surface of the first friction member and the second friction member facing the cam member.
  • the convex part or concave part is in a non-fitted state The opposite end of the convex portion or concave portion, characterized in that the inclined so as to contact the friction surface of the first friction member and the second friction member.
  • the friction surfaces of the first friction member and the second friction member are substantially parallel when the cam member is inclined in the non-fitted state.
  • the said convex part or recessed part is provided in the symmetrical position centering on the said shaft member.
  • the said convex part or recessed part is provided so that it may extend linearly in an orthogonal direction or a parallel direction with respect to the straight line orthogonal to the said shaft member and an up-down direction.
  • the said convex part or recessed part is the length which does not reach the outer peripheral end of the both surfaces of the said cam member, and the friction surface of a 1st friction member and a 2nd friction member.
  • the cam member is inclined when they are not fitted, and this inclination As a result, the end of the cam member located on the opposite side of the convex portion or the concave portion comes into contact with the friction surfaces of the first and second friction members to generate a friction torque. For this reason, stable friction torque can be generated. Further, since the convex portion or the concave portion is formed on both surfaces of the cam member and the friction surfaces of the first and second friction members, the friction portions are increased, and a stable friction torque can be applied.
  • the convex portion or the concave portion is formed on both surfaces of the cam member and the friction surfaces of the first and second friction members, the number of parts for generating the friction torque can be reduced. And since the convex part or recessed part is formed in the both surfaces of a cam member and the friction surface of a 1st and 2nd friction member in this way, a suction operation can be ensured, without a stroke becoming long. Thereby, it can prevent that a hinge apparatus becomes long in an axial direction.
  • FIG. 1 shows a hinge device according to an embodiment, wherein (a) is an end view of a state of attachment to a personal computer, (b) is a plan view of the second member at an opening angle of 0 °, and (c) is a longitudinal sectional view of (b). is there. (A) is a top view in the open angle of 180 degrees of a 2nd member, (b) is a longitudinal cross-sectional view of (a). The first friction member is shown, (a) is a plan view, (b) is a left side view, and (c) is a cross-sectional view taken along line E1-E1 of (b).
  • the cam member is shown, (a) is a left side view, (b) is an E2-E2 cross-sectional view of (a), and (c) is a right side view.
  • the second friction member is shown, (a) is a left side view, (b) is a sectional view taken along line E3-E3 of (c), and (c) is a right side view.
  • the 1st modification of a cam member is shown, (a) is a left view, (b) is E5-E5 sectional drawing of (a), (c) is a right view.
  • transformation form of a cam member is shown, (a) is a left view, (b) is E6-E6 sectional drawing of (a), (c) is a right view.
  • the 3rd modification of a cam member is shown, (a) is a left view, (b) is E7-E7 sectional drawing of (a), (c) is a right view.
  • the 4th modification of a cam member is shown, (a) is a left view, (b) is E4-E4 sectional view taken on the line of (a), (c) is a right view.
  • It is a longitudinal cross-sectional view which shows the hinge apparatus of another embodiment of this invention. It is a disassembled perspective view which shows the hinge apparatus of another embodiment of this invention. It is a perspective view of the notebook personal computer in which a hinge apparatus is used. It is a side view explaining the characteristic requested
  • (A), (b) is the top view and longitudinal cross-sectional view of the conventional hinge apparatus.
  • (A), (b) is a longitudinal cross-sectional view of another conventional hinge apparatus.
  • FIG. 1 to 10 show a hinge device 1 according to an embodiment of the present invention.
  • FIG. 1 is an exploded perspective view
  • FIG. 2 is a state with an opening angle of 0 °
  • FIG. 3 is a state with an opening angle of 180 °.
  • the hinge device 1 is provided at a hinge portion where a second member 120 as a display or a lid is attached to the first member 110 as a main body so as to be opened and closed.
  • the hinge device 1 includes a shaft member 2, a first friction member 3 and a second friction member 4, a cam member 5, and a biasing means 6.
  • the shaft member 2 is formed by a shaft body 21 and a shaft body 22 that extends integrally from one side surface of the shaft body 21. As shown in FIG. 2, the shaft body 21 is fixed to the second member 120 with screws 7. Therefore, when the second member 120 is rotated, the shaft member 2 rotates together with the second member 120.
  • the shaft body 22 is formed in a non-circular outline obtained by cutting a circle in parallel.
  • the shaft body 22 only needs to have a non-circular outer shape, and may have an outer shape obtained by D-cutting a circle, a rectangular shape, or an elliptical outer shape.
  • a pair of friction members sandwiching the cam member 5 is formed by the first friction member 3 and the second friction member 4.
  • the first friction member 3 is formed by a planar flange portion 31 on the bottom surface side and a bearing portion 32 that rises upright from the flange portion 31, and the flange portion 31 is the first member 110.
  • the first friction member 3 is a fixed side member.
  • the bearing portion 32 is raised from the first member 110.
  • a circular shaft hole 33 is formed in the bearing portion 32, and the shaft body 22 of the shaft member 2 passes through the shaft hole 33 in a rotatable manner.
  • the second friction member 4 has a circular outer shape as shown in FIGS. 2 and 3, and is connected to the first friction member 3 to be a fixed side member like the first friction member 3.
  • a connection piece 44 having a non-circular outer shape is projected from the second friction member 4 and the connection piece 44 is fitted to the first friction member 3.
  • a connecting hole 34 to be inserted is formed (see FIGS. 4 and 6).
  • the second friction member 4 is fixed to the first friction member 3 in a state of rising so as to be substantially parallel to the bearing portion 32 of the first friction member 3.
  • the second friction member 4 is formed with a circular shaft hole 43, and the shaft body 22 of the shaft member 2 penetrates through the shaft hole 43 in a rotatable manner.
  • the cam member 5 has a circular outer shape and is disposed so as to be sandwiched between the first friction member 3 and the second friction member 4.
  • the cam member 5 is formed with a non-circular shaft hole 53 corresponding to the shaft body 22 of the shaft member 2, and the shaft body 22 passes through the shaft hole 53.
  • the cam member 5 is coupled to the shaft member 2 so as to rotate integrally with the shaft member 2. Therefore, the cam member 5 is a rotation side member, and the cam member 5 rotates integrally with the shaft member 2 by rotating the second member 120. This rotation generates a friction torque between the first friction member 3 and the second friction member 4.
  • the urging means 6 is formed by laminating a plurality of leaf springs 6 a along the length direction of the shaft body 22 of the shaft member 2.
  • Each leaf spring 6a is formed with a non-circular shaft hole 6b corresponding to the shaft body 22 of the shaft member 2, and the shaft body 22 passes through the shaft hole 6b. Thereby, each leaf spring 6a rotates integrally with the rotation of the shaft member 2, that is, the rotation of the second member 120.
  • the urging means 6 may be formed by laminating a plurality of elastic bodies instead of the plurality of leaf springs 6a.
  • reference numeral 9 denotes a friction plate inserted between the shaft member 2 and the first friction member 3, and a non-circular shaft hole 9b corresponding to the shaft body 22 of the shaft member 2 is formed.
  • the shaft body 22 penetrates through the shaft hole 9b. Therefore, the friction plate 9 rotates integrally with the rotation of the shaft member 2. By this rotation, a friction torque is generated between the friction plate 9 and the first friction member 3.
  • reference numeral 10 denotes a stopper plate disposed outside the urging means 6.
  • the stopper plate 10 is formed with a non-circular shaft hole 10b corresponding to the shaft body 22 of the shaft member 2, and the shaft body 22 passes through the shaft hole 10b. Therefore, the stopper plate 10 rotates integrally with the rotation of the shaft member 2.
  • the shaft body 22 of the shaft member 2 passes through the stopper plate 10, and the plate spring 6a of the urging means 6 is bent by crimping the penetrating end 22a. As a result, the urging means 6 urges the second friction member 4, the cam member 5, the first friction member 3, and the friction plate 9 to contact each other.
  • the cam member 5, the first friction member 3, and the second friction member 4 are formed with convex portions 55 and concave portions 35 and 45.
  • the convex portions 55 are formed on both surfaces of the cam member 5, and the concave portions 35 and 45 are formed on the surfaces of the friction members 3 and 4 facing the cam member 5.
  • the convex portion 55 is formed on the first friction member 3 side surface 5a (hereinafter, right surface 5a) of the cam member 5 and the second friction member 4 side surface 5b (hereinafter, left surface 5b). Is formed.
  • the convex portions 55 on both surfaces 5a and 5b of the cam member 5 are formed at symmetrical positions around the shaft hole 53 with the shaft hole 53 in between, and the convex portion 55 on the right surface 5a and the convex portion 55 on the left surface 5b are cam members. 5 are formed at non-identical positions on both sides. That is, in the state of FIG.
  • the convex portion 55 on the surface 5 a side is located below the shaft hole 53, and the convex portion 55 on the surface 5 b side is located above the shaft hole 53 that is symmetrical to this.
  • the convex portions 55 of the both surfaces 5a and 5b are formed at symmetrical positions with the shaft body 22 as the center.
  • the portions where the convex portions 55 are not formed on both surfaces 5a and 5b of the cam member 5 are flat.
  • the convex portions 55 of both surfaces 5a and 5b of the cam member 5 linearly extend with a predetermined length along a direction orthogonal to the straight line orthogonal to the shaft body 22 of the shaft member 2 in the vertical direction. Due to the linearly extending shape, the convex portion 55 can slide while intersecting with concave portions 35 and 45, which will be described later, and the friction torque is generated by sliding with the concave portions 35 and 45. appear. Since each convex part 55 of both surfaces 5a and 5b of the cam member 5 has a top part 55a and a slope part 55b surrounding the top part 55a, slipping occurs by providing the slope part 55b surrounding the top part 55a. Suction operation is possible.
  • the concave portions 35 and 45 in the pair of friction members 3 and 4 are those into which the convex portions 55 of the cam member 5 are fitted, and as shown in FIGS. 2 and 4, the concave portion 35 is connected to the cam member 5 in the first friction member 3. As shown in FIGS. 2 and 6, the recess 45 is formed on the friction surface 4 a facing the cam member 5 in the second friction member. These concave portions 35 and 45 are formed so as to correspond to the convex portions 55 of the cam member 5, and are symmetrical positions about the shaft body 22 of the shaft member 2 passing through the respective shaft holes 33 and 43.
  • the concave portions 35 and 45 have bottom portions 35a and 45a and slope portions 35b and 45b surrounding the bottom portions 35a and 45a, and slip between the slope portions 35b and 45b and the slope portion 55b of the convex portion 55. As a result, a suction operation is possible.
  • the portions of the friction surfaces 3a, 4a of the pair of friction members 3, 4 where the recesses 35, 45 are not formed are flat.
  • the convex portion 55 on the cam member 5 side and the concave portions 35 and 45 of the pair of friction members 3 and 4 have an opening angle of the second member 120 of about 20 ° to 340 ° (in this embodiment, about 20 ° to 180 °). ), A friction torque is generated because it slides in a non-fitted state.
  • the suction operation is performed when the opening angle of the second member 120 is about 20 ° to 0 °, 340 ° to 0 ° (about 20 ° to 0 ° in this embodiment).
  • the operation and action of the cam member 5 and the friction members 3 and 4 will be described.
  • FIG. 2 shows a state in which the opening angle of the second member 120 is around 0 °.
  • the convex portion 55 of the right surface 5a of the cam member 5 is fitted into the concave portion 35 of the first friction member 3 and the cam member 5
  • the convex portion 55 of the left surface 5 b is fitted in the concave portion 45 of the second friction member 4. Thereby, the closed state of the second member 120 is maintained.
  • FIG. 3 shows a state in which the opening angle of the second member 120 is 180 °.
  • the opening angle is about 20 ° to 180 °
  • the convex portions 55 of the both surfaces 5a and 5b of the cam member 5 and the concave portions of the pair of friction members 3 and 4 are shown.
  • 35 and 45 are in a non-fitted state.
  • the cam member 5 has the convex portions 55 of both surfaces 5a and 5b in contact with the flat portions of the friction surfaces 3a and 4a of the pair of friction members 3 and 4, and the cam member 5 is brought into contact with the pair of friction members by this contact. Inclined between 3 and 4.
  • produces between the cam member 5 and a pair of friction members 3 and 4 by these contacts, the stable friction torque can be generated.
  • a gap that can be inclined is provided between the shaft hole 53 of the cam member 5 and the shaft body 22 of the shaft member 2.
  • the cam member 5 is inclined between the pair of friction members 3 and 4, so that the two convex portions 55 of the both surfaces 5 a and 5 b of the cam member 5 are in contact with the friction members 3 and 4,
  • the end portions 56 a and 56 b on the cam member 5 opposite to the convex portion 55 are in contact with the friction members 3 and 4. Therefore, the cam member 5 and the pair of friction members 3 and 4 are in contact with each other at four points, and the friction portions are increased. Thereby, a stable friction torque can be obtained.
  • the convex portions 55 of the both surfaces 5a and 5b of the cam member 5 are lengthened, the two convex portions 55 and the two end portions 56a and 56b come into contact with each other at a substantially triangular position. Can be kept parallel and stable friction torque can be obtained.
  • the recesses 35 and 45 generate a rotational force in a direction in which the recesses 35 and 45 are engaged with each other by the biasing force of the biasing means 6.
  • a suction operation occurs, and the second member 120 is closed in combination with its own weight.
  • reference numeral 36 denotes a locus in which the end portion 56 b on the right surface 5 a of the cam member 5 slides on the opposing surface 3 a of the first friction member 3.
  • reference numeral 46 denotes an end on the left surface 5 b of the cam member 5. This is a trajectory in which the portion 56 a slides on the friction surface 4 a of the second friction member 4.
  • the trajectories 36 and 46 are formed on the outer peripheral side of the concave portions 35 and 45 formed on the friction members 3 and 4, and the end portions 56 a and 56 b of the cam member 5 are formed on the concave portions 35 of the friction members 3 and 4. , 45 without passing through the plane portions of the friction members 3, 4.
  • trajectories 36 and 46 can be formed by setting the convex part 55 of the cam member 5, and the recessed parts 35 and 45 of a pair of friction members 3 and 4 to the length which does not reach these outer peripheral ends. Become.
  • the stroke can be reduced by about 40%. Thereby, it can prevent that the hinge apparatus 1 becomes long in an axial direction. Further, since the stroke can be reduced compared to the conventional apparatus of FIG. 16, the number of leaf springs 6a can be reduced to 2/3, so that the number of parts can be reduced.
  • two convex portions 55 are formed on each of both surfaces 5 a and 5 b of the cam member 5.
  • the two convex portions 55 of the both surfaces 5a and 5b are provided at symmetrical positions of the shaft body 22 of the shaft member 2.
  • the convex part 55 of each surface 5a, 5b is linearly extended in the parallel direction with respect to the shaft 22 and the straight line orthogonal to an up-down direction. 7 can obtain a stable friction torque, reduce the stroke, and reduce the number of parts.
  • two convex portions 55 are formed on each surface 5 a and 5 b of the cam member 5.
  • the two convex portions 55 on the both surfaces 5a and 5b are provided at symmetrical positions of the shaft body 22 of the shaft member 2 and extend linearly in a direction orthogonal to the straight line perpendicular to the shaft body 22 in the vertical direction.
  • the convex portions 55 of the both surfaces 5a and 5b are formed by pressing the cam member 5, whereby the cam member 5 can be reduced in weight.
  • the convex portion 55 of the left surface 5b is not provided at the symmetrical position with the shaft body 22 as the center, but is formed at a position shifted from the symmetrical position with respect to the convex portion 55 of the right surface 5a.
  • the convex portions 55 of both surfaces 5a and 5b both extend in a direction orthogonal to the straight line perpendicular to the shaft body 22 and the vertical direction, but the convex portion 55 of the left surface 5b is somewhat curved without extending linearly. It extends in. Even in such a structure, a stable friction torque can be obtained, the stroke can be reduced, and the number of parts can be reduced.
  • convex portions 55 are formed so as to be symmetrical with respect to the shaft body 22 with respect to both surfaces 5 a and 5 b of the cam member 5. All the convex portions 55 are arranged so as to extend on a straight line perpendicular to the shaft body 22 in the vertical direction. Even in such a structure, a stable friction torque can be obtained, the stroke can be reduced, and the number of parts can be reduced.
  • FIG. 11 and 12 show hinge devices 1A and 1B according to another embodiment of the present invention, respectively, and the same members as those of the hinge device 1 according to the above-described embodiment are denoted by the same reference numerals.
  • a hinge device 1A shown in FIG. 11 has a cam member 5 formed with a concave portion 57 and a pair of friction members 3 and 4 sandwiching the cam member 5 with convex portions 37 and 47.
  • Other configurations are hinge devices. Same as 1.
  • the concave portions 57 and the convex portions 37 and 47 are provided at symmetrical positions around the shaft body 22 of the shaft member 2 as in the convex portions 55 and the concave portions 35 and 45 in the hinge device 1 and are orthogonal to the shaft body 22 in the vertical direction. It is formed so as to extend linearly in a direction orthogonal to the straight line. That is, in the hinge device 1 ⁇ / b> A of this embodiment, the uneven portion is provided opposite to the hinge device 1. Even in such a configuration, the friction torque can be stabilized, and the number of parts can be reduced, so that the hinge device does not become longer in the axial direction.
  • the 12 uses a plurality of disc springs 6c as springs of the urging means 6.
  • the plurality of disc springs 6c are provided so as to be adjacent to each other by being reversed.
  • a partition plate 11 is provided between the urging means 6 and the second friction member 4 so that the disc spring 6 c does not directly contact the second friction member 4. Even in the case where such a disc spring 6c is used, the friction torque can be stabilized, and the hinge device that does not become long in the axial direction by reducing the number of parts can be obtained.
  • the cam member 5 may be connected to the first member 110 to be the fixed side, while the pair of friction members 3 and 4 may be connected to the first member 110 to be the rotating side.

Abstract

Provided is a hinge device that is not long in an axial direction, configured with fewer parts and a simple structure, and capable of stabilizing friction torque. The hinge device of the present invention comprises a cam member (5), friction members (3, 4) inserted into the cam member (5) in order for both side surfaces (5a, 5b) of the cam member (5) to face friction surfaces (3a, 4a), and a biasing means (6) for biasing in a direction in which the cam member (5) and the friction members (3, 4) come into contact with each other. A convex portion (55) and concave portions (35, 45), fitting with each other, are disposed at both side surfaces (5a, 5b) of the cam member (5) and counterface surfaces of the friction members (3, 4). The cam member (5) is inclined so that edges (56a, 56b) of opposite sides of the concave portions (35, 45) or the convex portion (55) come into contact with the friction surfaces of the friction members (3, 4) when the convex portion (55) and the concave portions (35, 45) do not fit with each other.

Description

ヒンジ装置Hinge device
　本発明は、ノート型パソコン、携帯電話機等に組み込まれるヒンジ装置であって、例えば、本体に対して蓋体を開閉させるため、蓋体を本体に対して回動可能に連結するヒンジ装置に関する。 The present invention relates to a hinge device incorporated in a notebook computer, a mobile phone, or the like, for example, a hinge device that pivotally connects a lid to the main body so as to open and close the lid with respect to the main body.
　図１３はノート型パソコン１００の一例を示し、本体（キーボード）が第１部材１１０、蓋体（ディスプレー）が第２部材１２０となっており、第２部材１２０が第１部材１１０に開閉可能に取り付けられている。第２部材１２０の開閉は、第１部材１１０に対して回動操作することにより行われ、第２部材１２０を第１部材１１０に回動可能に連結するため、これらの部材１１０，１２０がヒンジ装置１３０によって連結されている。 FIG. 13 shows an example of a notebook personal computer 100. The main body (keyboard) is a first member 110, the lid (display) is a second member 120, and the second member 120 can be opened and closed to the first member 110. It is attached. The opening and closing of the second member 120 is performed by rotating the first member 110, and the second member 120 is pivotally connected to the first member 110. Therefore, the members 110 and 120 are hinged. They are connected by a device 130.
　図１４は以上のノート型パソコン１００に要求される特性を説明する図であり、ディスプレイからなる第２部材１２０は、所定角度（２０～１８０°）範囲内においては、任意の角度で保持されるフリーストップ機能が要求される。又、全閉付近（０～２０°）では、第２部材１２０が自力で閉じる吸い込み動作が要求される。 FIG. 14 is a diagram for explaining the characteristics required for the notebook personal computer 100 described above. The second member 120 formed of a display is held at an arbitrary angle within a predetermined angle (20 to 180 °) range. A free stop function is required. Also, in the vicinity of full closure (0 to 20 °), a suction operation is required in which the second member 120 is closed by itself.
　図１５は、特許文献１に記載された従来のヒンジ装置２００を示し、吸い込み動作が可能となっている。図１５は第１部材１１０に対して第２部材１２０が閉じた角度０°の状態を示す。ヒンジ装置２００は、第１部材１１０にブラケットからなる摩擦部材２１０が立上がり状に固定され、第２部材１２０にカム部材２２０が取り付けられている。摩擦部材２１０及びカム部材２２０は相互に面接触している。第２部材１２０には、軸部材２３０がねじ２４０によって取り付けられており、軸部材２３０の軸部２３１が摩擦部材２１０及びカム部材２２０を貫通している。又、摩擦部材２１０と軸部材２３０との間には、摩擦板２５０が挟まれることにより摩擦トルクが発生している。 FIG. 15 shows a conventional hinge device 200 described in Patent Document 1, and a suction operation is possible. FIG. 15 illustrates a state where the second member 120 is closed with respect to the first member 110 at an angle of 0 °. In the hinge device 200, a friction member 210 including a bracket is fixed to the first member 110 in a rising shape, and a cam member 220 is attached to the second member 120. The friction member 210 and the cam member 220 are in surface contact with each other. A shaft member 230 is attached to the second member 120 with a screw 240, and a shaft portion 231 of the shaft member 230 passes through the friction member 210 and the cam member 220. Further, a friction torque is generated by the friction plate 250 being sandwiched between the friction member 210 and the shaft member 230.
　軸部材２３０の軸部２３１には、複数の皿ばねを重ね合わせて形成された付勢手段２７０が取り付けられる。皿ばねからなる付勢手段２７０はカム部材２２０を摩擦部材２１０に押し付けるように付勢する。付勢手段２７０の外側には、軸部材２３０の軸部２３１が貫通したワッシャ２８０が設けられ、ワッシャ２８０から抜け出た軸部材２３０の軸部２３１の先端部分を加締めることにより付勢手段２７０を撓ませ状態とする。これにより付勢手段２７０がカム部材２２０を付勢した状態となる。 The biasing means 270 formed by overlapping a plurality of disc springs is attached to the shaft portion 231 of the shaft member 230. The biasing means 270 made of a disc spring biases the cam member 220 so as to press it against the friction member 210. A washer 280 through which the shaft part 231 of the shaft member 230 passes is provided outside the biasing means 270, and the biasing means 270 is tightened by crimping the tip end portion of the shaft part 231 of the shaft member 230 that has come out of the washer 280. Let it be bent. As a result, the biasing means 270 biases the cam member 220.
　このような構造において、軸部材２３０の軸部２３１は、外形が平行カット、Ｄカット、矩形等の非円形となっている一方、この軸部２３１が貫通する摩擦部材２１０の軸孔は円形となっており、軸部材２３０は回転するが、摩擦部材２１０は回転することがない固定側となっている。これに対し、カム部材２２０の軸孔は軸部材２３０の軸孔２３１に相応した非円形となっており、この軸孔に軸部材２３０の軸部２３１が貫通することにより、カム部材２２０は軸部材２３０（すなわち第２部材１２０）と共に一体回転する。従って第２部材１２０が回動操作されると、カム部材２２０が摩擦部材２１０に対して回転してこれらが面接触している対向面が摩擦面となって摩擦力が発生するため、カム部材２２０の回転が停止し、第２部材１２０が任意の角度で保持される。 In such a structure, the shaft portion 231 of the shaft member 230 has a non-circular outer shape such as a parallel cut, a D cut, or a rectangle, while the shaft hole of the friction member 210 through which the shaft portion 231 passes is circular. Thus, the shaft member 230 rotates, but the friction member 210 does not rotate. On the other hand, the shaft hole of the cam member 220 is a non-circular shape corresponding to the shaft hole 231 of the shaft member 230, and the shaft portion 231 of the shaft member 230 passes through this shaft hole, so that the cam member 220 has a shaft hole. It rotates together with the member 230 (that is, the second member 120). Accordingly, when the second member 120 is rotated, the cam member 220 rotates with respect to the friction member 210 and the opposing surface in contact with the friction member 210 becomes a friction surface to generate a frictional force. The rotation of 220 stops, and the second member 120 is held at an arbitrary angle.
　これに加えて、カム部材２２０の摩擦部材２１０との対向面（摩擦面）には凸部２９１が形成され、摩擦部材２１０の対向面（摩擦面）には凹部２９２が形成されている。摩擦面に形成されているこれらの凸部２９１及び凹部２９２は第２部材１２０の開角度が２０°付近から対応し、開角度が０°のときに嵌合するように形成されるものである。又、凸部２９１及び凹部２９２の始端部及び終端部には、斜面部（図示省略）が形成されており、凸部２９１及び凹部２９２が嵌合可能位置に達すると、斜面部の間で滑りを生じるようになっている。第２部材１２０の閉じ作動により凸部２９１の斜面部及び凹部２９２の斜面部が接触すると、これらの間に発生する滑りによる回転トルクと第２部材１２０の自重とによってカム部材２２０が吸い込み動作し、これにより第２部材１２０が自力で閉じることができる。 In addition, a convex portion 291 is formed on the surface (friction surface) of the cam member 220 facing the friction member 210, and a concave portion 292 is formed on the surface (friction surface) of the friction member 210. These convex portions 291 and concave portions 292 formed on the friction surface correspond to an opening angle of the second member 120 from around 20 °, and are formed so as to be fitted when the opening angle is 0 °. . In addition, slope portions (not shown) are formed at the start and end portions of the convex portion 291 and the concave portion 292. When the convex portion 291 and the concave portion 292 reach a fitting position, they slide between the slope portions. It has come to produce. When the slope portion of the convex portion 291 and the slope portion of the concave portion 292 come into contact with each other by the closing operation of the second member 120, the cam member 220 performs a suction operation due to the rotational torque caused by the slip generated between them and the own weight of the second member 120. Thus, the second member 120 can be closed by itself.
　特許文献２～６には、摩擦トルクを大きくすると共に吸い込み動作を確保する構造が記載されている。これらの特許文献では、摩擦面の外径を大きくすることなく摩擦トルクを大きくするために摩擦面を多く設けて１面あたりの面圧を軽減するものである。又、吸い込み動作を確保するために凸部及び凹部を増加している。図１６はかかる構造となっているヒンジ装置３００を示す。 Patent Documents 2 to 6 describe structures that increase the friction torque and secure the suction operation. In these patent documents, in order to increase the friction torque without increasing the outer diameter of the friction surface, many friction surfaces are provided to reduce the surface pressure per surface. Further, the convex portions and the concave portions are increased in order to ensure the suction operation. FIG. 16 shows a hinge device 300 having such a structure.
　図１６のヒンジ装置３００は、摩擦部材２１０に第２の摩擦部材３１０を固定状態で組み付け、この摩擦部材２１０と第２の摩擦部材３１０との間にカム部材２２０を挟み込む構造となっている。さらに、第２の摩擦部材３１０の外側（付勢手段２７０側）に第２の摩擦部材３１０と面接触する第２のカム部材３２０を配置している。又、第２のカム部材３２０が第２の摩擦部材３１０と対向する面に凸部２９１を設け、第２の摩擦部材３１０が第２のカム部材３２０と対向する面に凹部２９２を設けると共に、カム部材２２０が摩擦部材２１０と対向する面に凸部２９１を設け、摩擦部材２１０がカム部材２２０と対向する面に凹部２９２を設けて吸い込み動作を行うようになっている。図１６（ａ）は第２部材１２０の開角度が０°の状態を示し、この状態では凸部２９１及び凹部２９２が嵌合している。図１６（ｂ）は第２部材１２０の開角度が９０°の状態を示し、凸部２９１及び凹部２９２が非嵌合状態となっている。 16 has a structure in which the second friction member 310 is assembled to the friction member 210 in a fixed state, and the cam member 220 is sandwiched between the friction member 210 and the second friction member 310. Further, a second cam member 320 that is in surface contact with the second friction member 310 is disposed outside the second friction member 310 (on the biasing means 270 side). The second cam member 320 is provided with a convex portion 291 on the surface facing the second friction member 310, the second friction member 310 is provided with a concave portion 292 on the surface facing the second cam member 320, The cam member 220 is provided with a convex portion 291 on the surface facing the friction member 210, and the friction member 210 is provided with a concave portion 292 on the surface facing the cam member 220 to perform the suction operation. FIG. 16A shows a state in which the opening angle of the second member 120 is 0 °. In this state, the convex portion 291 and the concave portion 292 are fitted. FIG. 16B shows a state in which the opening angle of the second member 120 is 90 °, and the convex portion 291 and the concave portion 292 are not fitted.
　図１６のヒンジ装置３００では、凹凸部２９１，２９２が形成されて対向している第２のカム部材３２０と第２の摩擦部材３１０との対向面、凹凸部２９１，２９２が形成されることなく平面で対向している平面第２の摩擦部材３１０とカム部材２２０との対向面、凹凸部２０１，２９２が形成されて対向しているカム部材２２０と摩擦部材２１０との対向面、凹凸部２９１，２９２が形成されることなく平面で対向している摩擦部材２１０と摩擦板２５０の対向面の４面を摩擦面とするものである。 In the hinge device 300 of FIG. 16, the opposing surfaces of the second cam member 320 and the second friction member 310 facing each other with the uneven portions 291 and 292 formed, without the uneven portions 291 and 292 being formed. The opposing surface of the flat second friction member 310 and the cam member 220 facing each other in a plane, the opposing surface of the cam member 220 and the friction member 210 facing each other formed with the uneven portions 201 and 292, and the uneven portion 291. , 292 are not formed, and four surfaces of the facing surfaces of the friction member 210 and the friction plate 250 facing each other in a plane are used as friction surfaces.
特許第４３８６８６４号公報Japanese Patent No. 4386864 実用新案登録第３０１１５６８号公報Utility Model Registration No. 30111568 特開２００５－１３３７５９号公報JP 2005-133759 A 特開２００６－１７３１３号公報JP 2006-17313 A 特開２００２－３１０１２９号公報JP 2002-310129 A ＷＯ２００４－２７２７４号公報WO2004-27274
　しかしながら、図１５のヒンジ装置２００では、凸部２９１と凹部２９０とが非嵌合状態のとき、凸部２９１だけが摩擦部材２１０の対向面（摩擦面）に接触し摺動して摩擦トルクを発生するが、カム部材２２０が傾くことにより、カム部材２２０と摩擦部材２１０の接触状態が不安定となり、付勢手段２７０が軸方向に安定して撓まないで　斜めに撓むという問題が発生する。この結果、付勢力が不安定となり、摩擦トルクが安定しない欠点がある However, in the hinge device 200 of FIG. 15, when the convex portion 291 and the concave portion 290 are not fitted, only the convex portion 291 contacts and slides against the opposing surface (friction surface) of the friction member 210 to generate friction torque. However, when the cam member 220 is tilted, the contact state between the cam member 220 and the friction member 210 becomes unstable, and the biasing means 270 does not bend stably in the axial direction, causing a problem of bending obliquely. To do. As a result, the biasing force becomes unstable and the friction torque is not stable.
　図１６のヒンジ装置３００では、凸部２９１を第２のカム部材３２０及びカム部材２２０のそれぞれに設け、凹部２９２を第２の摩擦部材３１０及び摩擦部材２１０のそれぞれに設けており、しかもこれらが直列に配置されるため、軸方向に長くなる問題がある。又、第２のカム部材３２０及び第２の摩擦部材３１０を必要とするため、部品点数が多く、構造が複雑となっている。 In the hinge device 300 of FIG. 16, the convex portion 291 is provided in each of the second cam member 320 and the cam member 220, and the concave portion 292 is provided in each of the second friction member 310 and the friction member 210. Since they are arranged in series, there is a problem that they become longer in the axial direction. Further, since the second cam member 320 and the second friction member 310 are required, the number of parts is large and the structure is complicated.
　さらに、吸い込み動作する際のストロークが長くなっていることから付勢手段を構成するばねのストロークも大きくなるため、耐久性を確保するためにはばねの数を多くする必要がある。すなわち、凸部２９１の高さをＨとした場合、ヒンジ装置３００の全体では２Ｈのストロークとなり、このストロークに対応するため、ばねの数は図１５のヒンジ装置２００の２倍必要となっている。このようにばね数が増えることにより、構造がさらに複雑となる。 Furthermore, since the stroke during the suction operation is long, the stroke of the spring constituting the urging means is also large. Therefore, it is necessary to increase the number of springs in order to ensure durability. That is, when the height of the convex portion 291 is H, the entire hinge device 300 has a stroke of 2H, and the number of springs is twice that of the hinge device 200 of FIG. 15 to accommodate this stroke. . As the number of springs increases in this way, the structure becomes more complicated.
　本発明は、このような従来の問題点を考慮してなされたものであり、軸方向に長くなることなく、部品点数を少なくすることができ、簡単な構造であるにもかかわらず摩擦トルクを安定させることができ、且つ吸い込み動作を確保することが可能なヒンジ装置を提供することを目的とする。 The present invention has been made in consideration of such conventional problems, and the number of parts can be reduced without being elongated in the axial direction, and the friction torque can be reduced despite the simple structure. It is an object of the present invention to provide a hinge device that can be stabilized and can secure a suction operation.
　本発明のヒンジ装置は、第１部材と第２部材とを相対回転可能に連結するヒンジ装置であって、一方の部材に固定される第１摩擦部材と、この第１摩擦部材に回転自在に支持されて他方の部材が固定される軸部材と、この軸部材に回転拘束されて軸方向移動可能に設けられるカム部材と、このカム部材を挟み前記第１摩擦部材に対向した状態で固定される第２摩擦部材と、前記第１摩擦部材とカム部材と第２摩擦部材とが接触する方向に付勢する付勢手段とを備え、前記カム部材の両面の非同一位置に凸部もしくは凹部が形成され、前記第１摩擦部材及び第２摩擦部材の前記カム部材と対向する摩擦面に前記カム部材の凸部もしくは凹部に相互に嵌合する凸部もしくは凹部が形成され、前記カム部材は、凸部もしくは凹部が非嵌合状態のときに凸部もしくは凹部の反対側の端部が前記第１摩擦部材及び第２摩擦部材の摩擦面に接触するように傾斜することを特徴とする。 A hinge device according to the present invention is a hinge device that connects a first member and a second member so as to be relatively rotatable, and includes a first friction member fixed to one member, and the first friction member rotatably. A shaft member that is supported and to which the other member is fixed, a cam member that is rotationally restrained by the shaft member and that can be moved in the axial direction, and is fixed in a state of being opposed to the first friction member with the cam member interposed therebetween. A second friction member, and a biasing means for biasing the first friction member, the cam member, and the second friction member in contact with each other, and a convex portion or a concave portion at non-identical positions on both surfaces of the cam member. A convex portion or a concave portion that fits into the convex portion or the concave portion of the cam member is formed on the friction surface of the first friction member and the second friction member facing the cam member. , The convex part or concave part is in a non-fitted state The opposite end of the convex portion or concave portion, characterized in that the inclined so as to contact the friction surface of the first friction member and the second friction member.
　この場合、前記非嵌合状態で前記カム部材が傾斜しているとき、前記第１摩擦部材及び第２摩擦部材の摩擦面が略平行であることが好ましい。 In this case, it is preferable that the friction surfaces of the first friction member and the second friction member are substantially parallel when the cam member is inclined in the non-fitted state.
　又、前記凸部もしくは凹部は、前記軸部材を中心とした対称位置に設けられていることが好ましい。 Moreover, it is preferable that the said convex part or recessed part is provided in the symmetrical position centering on the said shaft member.
　又、前記凸部もしくは凹部は、前記軸部材と上下方向に直交する直線に対して直交方向又は平行方向に直線的に延びるように設けられていることが好ましい。 Moreover, it is preferable that the said convex part or recessed part is provided so that it may extend linearly in an orthogonal direction or a parallel direction with respect to the straight line orthogonal to the said shaft member and an up-down direction.
　又、前記凸部もしくは凹部は、前記カム部材の両面及び第１摩擦部材及び第２摩擦部材の摩擦面の外周端に達しない長さとなっていることが好ましい。 Moreover, it is preferable that the said convex part or recessed part is the length which does not reach the outer peripheral end of the both surfaces of the said cam member, and the friction surface of a 1st friction member and a 2nd friction member.
　本発明によれば、カム部材の両面及び第１摩擦部材、第２摩擦部材の摩擦面に凸部もしくは凹部を形成することにより、これらが非嵌合状態のときカム部材が傾斜し、この傾斜によって凸部もしくは凹部と反対側に位置しているカム部材の端部が第１及び第２摩擦部材の摩擦面と接触して摩擦トルクを発生させる。このため、安定した摩擦トルクを発生させることができる。又、凸部もしくは凹部は、カム部材の両面及び第１及び第２の摩擦部材の摩擦面に形成されているため、摩擦部分が多くなっており、安定した摩擦トルクを作用させることができる。 According to the present invention, by forming convex portions or concave portions on both surfaces of the cam member and the friction surfaces of the first friction member and the second friction member, the cam member is inclined when they are not fitted, and this inclination As a result, the end of the cam member located on the opposite side of the convex portion or the concave portion comes into contact with the friction surfaces of the first and second friction members to generate a friction torque. For this reason, stable friction torque can be generated. Further, since the convex portion or the concave portion is formed on both surfaces of the cam member and the friction surfaces of the first and second friction members, the friction portions are increased, and a stable friction torque can be applied.
　又、凸部もしくは凹部をカム部材の両面及び第１及び第２摩擦部材の摩擦面に形成していることから、摩擦トルクを発生するための部品点数を少なくすることができる。そして、このように凸部もしくは凹部をカム部材の両面及び第１及び第２摩擦部材の摩擦面に形成していることから、ストロークが長くなることがなく吸い込み動作を確保できる。これによりヒンジ装置が軸方向に長くなることを防止できる。 Further, since the convex portion or the concave portion is formed on both surfaces of the cam member and the friction surfaces of the first and second friction members, the number of parts for generating the friction torque can be reduced. And since the convex part or recessed part is formed in the both surfaces of a cam member and the friction surface of a 1st and 2nd friction member in this way, a suction operation can be ensured, without a stroke becoming long. Thereby, it can prevent that a hinge apparatus becomes long in an axial direction.
本発明の一実施形態のヒンジ装置を示す分解斜視図である。It is a disassembled perspective view which shows the hinge apparatus of one Embodiment of this invention. 一実施形態のヒンジ装置を示し、（ａ）はパソコンへの取り付け状態の端面図、（ｂ）は第２部材の開角度０°における平面図、（ｃ）は（ｂ）の縦断面図である。1 shows a hinge device according to an embodiment, wherein (a) is an end view of a state of attachment to a personal computer, (b) is a plan view of the second member at an opening angle of 0 °, and (c) is a longitudinal sectional view of (b). is there. （ａ）は第２部材の開角度１８０°における平面図、（ｂ）は（ａ）の縦断面図である。(A) is a top view in the open angle of 180 degrees of a 2nd member, (b) is a longitudinal cross-sectional view of (a). 第１摩擦部材を示し、（ａ）は平面図、（ｂ）は左側面図、（ｃ）は（ｂ）のＥ１－Ｅ１線断面図である。The first friction member is shown, (a) is a plan view, (b) is a left side view, and (c) is a cross-sectional view taken along line E1-E1 of (b). カム部材を示し、（ａ）は左側面図、（ｂ）は（ａ）のＥ２－Ｅ２断面図、（ｃ）は右側面図である。The cam member is shown, (a) is a left side view, (b) is an E2-E2 cross-sectional view of (a), and (c) is a right side view. 第２摩擦部材を示し、（ａ）は左側面図、（ｂ）は（ｃ）のＥ３－Ｅ３線断面図、（ｃ）は右側面図である。The second friction member is shown, (a) is a left side view, (b) is a sectional view taken along line E3-E3 of (c), and (c) is a right side view. カム部材の第１変形形態を示し、（ａ）は左側面図、（ｂ）は（ａ）のＥ５－Ｅ５断面図、（ｃ）は右側面図である。The 1st modification of a cam member is shown, (a) is a left view, (b) is E5-E5 sectional drawing of (a), (c) is a right view. カム部材の第２変形形態を示し、（ａ）は左側面図、（ｂ）は（ａ）のＥ６－Ｅ６断面図、（ｃ）は右側面図である。The 2nd deformation | transformation form of a cam member is shown, (a) is a left view, (b) is E6-E6 sectional drawing of (a), (c) is a right view. カム部材の第３変形形態を示し、（ａ）は左側面図、（ｂ）は（ａ）のＥ７－Ｅ７断面図、（ｃ）は右側面図である。The 3rd modification of a cam member is shown, (a) is a left view, (b) is E7-E7 sectional drawing of (a), (c) is a right view. カム部材の第４変形形態を示し、（ａ）は左側面図、（ｂ）は（ａ）のＥ４－Ｅ４線断面図、（ｃ）は右側面図である。The 4th modification of a cam member is shown, (a) is a left view, (b) is E4-E4 sectional view taken on the line of (a), (c) is a right view. 本発明の別の実施形態のヒンジ装置を示す縦断面図である。It is a longitudinal cross-sectional view which shows the hinge apparatus of another embodiment of this invention. 本発明のさらに別の実施形態のヒンジ装置を示す分解斜視図である。It is a disassembled perspective view which shows the hinge apparatus of another embodiment of this invention. ヒンジ装置が用いられるノート型パソコンの斜視図である。It is a perspective view of the notebook personal computer in which a hinge apparatus is used. ヒンジ装置に要求される特性を説明する側面図である。It is a side view explaining the characteristic requested | required of a hinge apparatus. （ａ）、（ｂ）は従来のヒンジ装置の平面図及び縦断面図である。(A), (b) is the top view and longitudinal cross-sectional view of the conventional hinge apparatus. （ａ）、（ｂ）は別の従来のヒンジ装置の縦断面図である。(A), (b) is a longitudinal cross-sectional view of another conventional hinge apparatus.
　図１～図１０は本発明の一実施形態のヒンジ装置１を示し、図１は分解斜視図、図２は開角度０°の状態、図３は開角度１８０°の状態である。 1 to 10 show a hinge device 1 according to an embodiment of the present invention. FIG. 1 is an exploded perspective view, FIG. 2 is a state with an opening angle of 0 °, and FIG. 3 is a state with an opening angle of 180 °.
　ヒンジ装置１は図１３及び図１４に示すヒンジ装置１３０と同様に、本体としての第１部材１１０に対し、ディスプレイや蓋体としての第２部材１２０を開閉自在に取り付けるヒンジ部分に設けられる。 Similarly to the hinge device 130 shown in FIGS. 13 and 14, the hinge device 1 is provided at a hinge portion where a second member 120 as a display or a lid is attached to the first member 110 as a main body so as to be opened and closed.
　図１に示すようにヒンジ装置１は、軸部材２と、第１摩擦部材３及び第２摩擦部材４と、カム部材５と、付勢手段６とを備えている。 As shown in FIG. 1, the hinge device 1 includes a shaft member 2, a first friction member 3 and a second friction member 4, a cam member 5, and a biasing means 6.
　軸部材２はシャフト本体２１と、シャフト本体２１の一側の側面から一体に延びる軸体２２とによって形成されている。シャフト本体２１は図２に示すように、第２部材１２０にねじ７によって固定される。従って、第２部材１２０が回動操作されると、軸部材２は第２部材１２０と一体となって回転する。軸体２２は円を平行カットした非円形の外形に形成されている。軸体２２は外形が非円形であれば良く、円をＤカットした外形や矩形状、楕円形状の外形であっても良い。 The shaft member 2 is formed by a shaft body 21 and a shaft body 22 that extends integrally from one side surface of the shaft body 21. As shown in FIG. 2, the shaft body 21 is fixed to the second member 120 with screws 7. Therefore, when the second member 120 is rotated, the shaft member 2 rotates together with the second member 120. The shaft body 22 is formed in a non-circular outline obtained by cutting a circle in parallel. The shaft body 22 only needs to have a non-circular outer shape, and may have an outer shape obtained by D-cutting a circle, a rectangular shape, or an elliptical outer shape.
　第１摩擦部材３及び第２摩擦部材４によってカム部材５を挟む一対の摩擦部材が形成される。第１摩擦部材３は図４に示すように、底面側の平面状のフランジ部３１と、フランジ部３１から直立状に立ち上がる軸受部３２とによって形成されており、フランジ部３１が第１部材１１０にねじ８によって固定される。これにより第１摩擦部材３は固定側部材となっている。この固定状態では、軸受部３２は第１部材１１０から立ち上がった状態となっている。軸受部３２には円形の軸孔３３が形成されており、軸孔３３に軸部材２の軸体２２が回転可能に貫通する。 A pair of friction members sandwiching the cam member 5 is formed by the first friction member 3 and the second friction member 4. As shown in FIG. 4, the first friction member 3 is formed by a planar flange portion 31 on the bottom surface side and a bearing portion 32 that rises upright from the flange portion 31, and the flange portion 31 is the first member 110. Are fixed by screws 8. Thus, the first friction member 3 is a fixed side member. In this fixed state, the bearing portion 32 is raised from the first member 110. A circular shaft hole 33 is formed in the bearing portion 32, and the shaft body 22 of the shaft member 2 passes through the shaft hole 33 in a rotatable manner.
　第２摩擦部材４は図２及び図３に示すように外形が円形となっており、第１摩擦部材３に連結されることにより第１摩擦部材３と同様に固定側部材となっている。第２摩擦部材４を第１摩擦部材３に連結するため、第２摩擦部材４に非円形の外形の連結片４４が突出されると共に第１摩擦部材３には連結片４４が嵌合状態で挿入される連結孔３４が形成されている（図４及び図６参照）。第１摩擦部材３に連結されることにより、第２摩擦部材４は第１摩擦部材３の軸受部３２と略平行となるように立ち上がった状態で第１摩擦部材３に固定される。第２摩擦部材４には、第１摩擦部材３と同様に円形の軸孔４３が形成されており、この軸孔４３に軸部材２の軸体２２が回転可能に貫通する。 The second friction member 4 has a circular outer shape as shown in FIGS. 2 and 3, and is connected to the first friction member 3 to be a fixed side member like the first friction member 3. In order to connect the second friction member 4 to the first friction member 3, a connection piece 44 having a non-circular outer shape is projected from the second friction member 4 and the connection piece 44 is fitted to the first friction member 3. A connecting hole 34 to be inserted is formed (see FIGS. 4 and 6). By being connected to the first friction member 3, the second friction member 4 is fixed to the first friction member 3 in a state of rising so as to be substantially parallel to the bearing portion 32 of the first friction member 3. Similar to the first friction member 3, the second friction member 4 is formed with a circular shaft hole 43, and the shaft body 22 of the shaft member 2 penetrates through the shaft hole 43 in a rotatable manner.
　図２及び図３に示すようにカム部材５は外形が円形となっており、第１摩擦部材３及び第２摩擦部材４に挟まれるように配置される。図５に示すように、カム部材５には軸部材２の軸体２２に相応した非円形の軸孔５３が形成されており、この軸孔５３に軸体２２が貫通する。このことによりカム部材５は軸部材２と一体回転するように軸部材２に連結される。従って、カム部材５は回転側部材となっており、第２部材１２０を回動操作することによりカム部材５は軸部材２と一体となって回転する。この回転により第１摩擦部材３及び第２摩擦部材４との間に摩擦トルクが発生する。 2 and 3, the cam member 5 has a circular outer shape and is disposed so as to be sandwiched between the first friction member 3 and the second friction member 4. As shown in FIG. 5, the cam member 5 is formed with a non-circular shaft hole 53 corresponding to the shaft body 22 of the shaft member 2, and the shaft body 22 passes through the shaft hole 53. Thus, the cam member 5 is coupled to the shaft member 2 so as to rotate integrally with the shaft member 2. Therefore, the cam member 5 is a rotation side member, and the cam member 5 rotates integrally with the shaft member 2 by rotating the second member 120. This rotation generates a friction torque between the first friction member 3 and the second friction member 4.
　付勢手段６は複数の板ばね６ａを軸部材２の軸体２２の長さ方向に沿って積層状態とすることにより形成されている。それぞれの板ばね６ａには軸部材２の軸体２２に相応した非円形の軸孔６ｂが形成されており、この軸孔６ｂに軸体２２が貫通する。これによりそれぞれの板ばね６ａは軸部材２の回転、すなわち第２部材１２０の回動と一体となって回転する。なお、複数の板ばね６ａに代えて複数の弾性体を積層させることにより付勢手段６としても良い。 The urging means 6 is formed by laminating a plurality of leaf springs 6 a along the length direction of the shaft body 22 of the shaft member 2. Each leaf spring 6a is formed with a non-circular shaft hole 6b corresponding to the shaft body 22 of the shaft member 2, and the shaft body 22 passes through the shaft hole 6b. Thereby, each leaf spring 6a rotates integrally with the rotation of the shaft member 2, that is, the rotation of the second member 120. The urging means 6 may be formed by laminating a plurality of elastic bodies instead of the plurality of leaf springs 6a.
　図１及び図２において、符号９は軸部材２と第１摩擦部材３との間に挿入された摩擦板であり、軸部材２の軸体２２に相応した非円形の軸孔９ｂが形成されており、この軸孔９ｂに軸体２２が貫通する。従って、摩擦板９は軸部材２の回転と一体となって回転する。この回転により摩擦板９と第１摩擦部材３との間に摩擦トルクが発生する。 1 and 2, reference numeral 9 denotes a friction plate inserted between the shaft member 2 and the first friction member 3, and a non-circular shaft hole 9b corresponding to the shaft body 22 of the shaft member 2 is formed. The shaft body 22 penetrates through the shaft hole 9b. Therefore, the friction plate 9 rotates integrally with the rotation of the shaft member 2. By this rotation, a friction torque is generated between the friction plate 9 and the first friction member 3.
　図１及び図２において、符号１０は付勢手段６の外側に配置されるストッパプレートである。ストッパプレート１０には軸部材２の軸体２２に相応した非円形の軸孔１０ｂが形成されており、軸孔１０ｂに軸体２２が貫通する。従って、ストッパプレート１０は軸部材２の回転と一体となって回転する。軸部材２の軸体２２はストッパプレート１０を貫通しており、その貫通端２２ａを加締めることにより付勢手段６の板ばね６ａを撓ませた状態とする。これにより付勢手段６は第２摩擦部材４、カム部材５、第１摩擦部材３及び摩擦板９が相互に接触するように付勢する。 1 and 2, reference numeral 10 denotes a stopper plate disposed outside the urging means 6. The stopper plate 10 is formed with a non-circular shaft hole 10b corresponding to the shaft body 22 of the shaft member 2, and the shaft body 22 passes through the shaft hole 10b. Therefore, the stopper plate 10 rotates integrally with the rotation of the shaft member 2. The shaft body 22 of the shaft member 2 passes through the stopper plate 10, and the plate spring 6a of the urging means 6 is bent by crimping the penetrating end 22a. As a result, the urging means 6 urges the second friction member 4, the cam member 5, the first friction member 3, and the friction plate 9 to contact each other.
　この実施形態においては、カム部材５、第１摩擦部材３及び第２摩擦部材４には凸部５５及び凹部３５，４５が形成されている。凸部５５はカム部材５の両面に形成され、凹部３５，４５は摩擦部材３，４におけるカム部材５との対向面に形成されている。 In this embodiment, the cam member 5, the first friction member 3, and the second friction member 4 are formed with convex portions 55 and concave portions 35 and 45. The convex portions 55 are formed on both surfaces of the cam member 5, and the concave portions 35 and 45 are formed on the surfaces of the friction members 3 and 4 facing the cam member 5.
　図５に示すように、凸部５５はカム部材５の第１摩擦部材３側の面５ａ（以下、右面５ａ）に形成されると共に第２摩擦部材４側の面５ｂ（以下、左面５ｂ）に形成されている。カム部材５の両面５ａ及び５ｂの凸部５５は軸孔５３を挟んで軸孔５３を中心とした対称位置に形成されており、右面５ａの凸部５５及び左面５ｂの凸部５５はカム部材５の両面の非同一位置に形成されている。すなわち図５の状態では、面５ａ側の凸部５５が軸孔５３の下側に位置し、面５ｂ側の凸部５５はこれと対称位置となる軸孔５３の上側に位置している。ここで軸孔５３には軸部材２の軸体２２が貫通することから、両面５ａ，５ｂの凸部５５は、軸体２２を中心とした対称位置に形成されるようになっている。カム部材５の両面５ａ，５ｂにおける凸部５５が形成されていない部分は平面となっている。 As shown in FIG. 5, the convex portion 55 is formed on the first friction member 3 side surface 5a (hereinafter, right surface 5a) of the cam member 5 and the second friction member 4 side surface 5b (hereinafter, left surface 5b). Is formed. The convex portions 55 on both surfaces 5a and 5b of the cam member 5 are formed at symmetrical positions around the shaft hole 53 with the shaft hole 53 in between, and the convex portion 55 on the right surface 5a and the convex portion 55 on the left surface 5b are cam members. 5 are formed at non-identical positions on both sides. That is, in the state of FIG. 5, the convex portion 55 on the surface 5 a side is located below the shaft hole 53, and the convex portion 55 on the surface 5 b side is located above the shaft hole 53 that is symmetrical to this. Here, since the shaft body 22 of the shaft member 2 passes through the shaft hole 53, the convex portions 55 of the both surfaces 5a and 5b are formed at symmetrical positions with the shaft body 22 as the center. The portions where the convex portions 55 are not formed on both surfaces 5a and 5b of the cam member 5 are flat.
　カム部材５の両面５ａ，５ｂの凸部５５は、軸部材２の軸体２２と上下方向に直交する直線に対して直交する方向に沿って所定長さで直線的に延びている。このように直線的に延びた形状となっていることにより、凸部５５は後述する凹部３５，４５と交差しながら摺動することができ、この凹部３５，４５との摺動によって摩擦トルクが発生する。カム部材５の両面５ａ，５ｂのそれぞれの凸部５５は、頂部５５ａと、頂部５５ａを囲む斜面部５５ｂとを有しており、頂部５５ａを囲む斜面部５５ｂを設けることにより滑りを生じるため、吸い込み動作が可能となっている。 The convex portions 55 of both surfaces 5a and 5b of the cam member 5 linearly extend with a predetermined length along a direction orthogonal to the straight line orthogonal to the shaft body 22 of the shaft member 2 in the vertical direction. Due to the linearly extending shape, the convex portion 55 can slide while intersecting with concave portions 35 and 45, which will be described later, and the friction torque is generated by sliding with the concave portions 35 and 45. appear. Since each convex part 55 of both surfaces 5a and 5b of the cam member 5 has a top part 55a and a slope part 55b surrounding the top part 55a, slipping occurs by providing the slope part 55b surrounding the top part 55a. Suction operation is possible.
　一対の摩擦部材３，４における凹部３５，４５はカム部材５の凸部５５が嵌合するものであり、図２及び図４に示すように凹部３５は第１摩擦部材３におけるカム部材５と対向した摩擦面３ａに形成され、図２及び図６に示すように凹部４５は第２摩擦部材におけるカム部材５と対向した摩擦面４ａに形成されている。これらの凹部３５，４５は、カム部材５の凸部５５に対応するように形成されるものであり、それぞれの軸孔３３，４３を貫通する軸部材２の軸体２２を中心とした対称位置に形成されていると共に、凸部５５と同じ長さを有して軸部材２の軸体２２と上下方向に直交する直線に対して直交する方向に直線的に延びている。さらに、凹部３５，４５は底部３５ａ，４５ａと、底部３５ａ，４５ａを囲む斜面部３５ｂ，４５ｂとを有しており、斜面部３５ｂ，４５ｂと凸部５５の斜面部５５ｂとの間で滑りを生じることにより吸い込み動作が可能となっている。一対の摩擦部材３，４の摩擦面３ａ，４ａにおける凹部３５，４５が形成されていない部分は平面となっている。 The concave portions 35 and 45 in the pair of friction members 3 and 4 are those into which the convex portions 55 of the cam member 5 are fitted, and as shown in FIGS. 2 and 4, the concave portion 35 is connected to the cam member 5 in the first friction member 3. As shown in FIGS. 2 and 6, the recess 45 is formed on the friction surface 4 a facing the cam member 5 in the second friction member. These concave portions 35 and 45 are formed so as to correspond to the convex portions 55 of the cam member 5, and are symmetrical positions about the shaft body 22 of the shaft member 2 passing through the respective shaft holes 33 and 43. And has the same length as the convex portion 55 and linearly extends in a direction perpendicular to the shaft 22 of the shaft member 2 and a straight line perpendicular to the vertical direction. Further, the concave portions 35 and 45 have bottom portions 35a and 45a and slope portions 35b and 45b surrounding the bottom portions 35a and 45a, and slip between the slope portions 35b and 45b and the slope portion 55b of the convex portion 55. As a result, a suction operation is possible. The portions of the friction surfaces 3a, 4a of the pair of friction members 3, 4 where the recesses 35, 45 are not formed are flat.
　以上のカム部材５側の凸部５５及び一対の摩擦部材３，４の凹部３５，４５は、第２部材１２０の開角度が約２０°～３４０°（この実施形態では約２０°～１８０°）のときに、非嵌合状態となって摺動するため摩擦トルクを発生する。又、第２部材１２０の開角度が約２０°～０°、３４０°～０°（この実施形態では約２０°～０°）のときに吸い込み動作を行う。以下、カム部材５及び摩擦部材３，４の動作及び作用を説明する。 The convex portion 55 on the cam member 5 side and the concave portions 35 and 45 of the pair of friction members 3 and 4 have an opening angle of the second member 120 of about 20 ° to 340 ° (in this embodiment, about 20 ° to 180 °). ), A friction torque is generated because it slides in a non-fitted state. The suction operation is performed when the opening angle of the second member 120 is about 20 ° to 0 °, 340 ° to 0 ° (about 20 ° to 0 ° in this embodiment). Hereinafter, the operation and action of the cam member 5 and the friction members 3 and 4 will be described.
　図２は第２部材１２０の開角度が０°付近の状態を示し、この状態ではカム部材５の右面５ａの凸部５５が第１摩擦部材３の凹部３５に嵌合すると共にカム部材５の左面５ｂの凸部５５が第２摩擦部材４の凹部４５に嵌合している。これにより第２部材１２０の閉じ状態が維持されている。 FIG. 2 shows a state in which the opening angle of the second member 120 is around 0 °. In this state, the convex portion 55 of the right surface 5a of the cam member 5 is fitted into the concave portion 35 of the first friction member 3 and the cam member 5 The convex portion 55 of the left surface 5 b is fitted in the concave portion 45 of the second friction member 4. Thereby, the closed state of the second member 120 is maintained.
　図３は第２部材１２０の開角度が１８０°の状態を示し、約２０°～１８０°の状態ではカム部材５の両面５ａ，５ｂの凸部５５と、一対の摩擦部材３，４の凹部３５，４５が非嵌合状態となっている。この状態では、カム部材５は両面５ａ，５ｂの凸部５５が一対の摩擦部材３，４の摩擦面３ａ，４ａにおける平面部分に接触しており、この接触によってカム部材５は一対の摩擦部材３，４の間で傾斜している。この傾斜状態では、カム部材５のそれぞれの凸部５５の反対側の端部が、対向している摩擦部材３，４の平面部分に接触する。すなわち、図３に示すようにカム部材５の右面５ａの凸部５５と反対側となっている左面５ｂの端部５６ａが第２摩擦部材４の摩擦面４ａにおける平面部分に接触し、カム部材５の左面５ｂの凸部５５と反対側となっている右面５ａの端部５６ｂが第１摩擦部材３の摩擦面３ａにおける平面部分に接触している。そして、これらの接触によってカム部材５と一対の摩擦部材３，４との間で摩擦トルクが発生するため、安定した摩擦トルクを発生させることができる。なお、カム部材５の傾斜を可能とするため、カム部材５の軸孔５３と軸部材２の軸体２２との間には、傾斜可能なだけの隙間が設けられている。 FIG. 3 shows a state in which the opening angle of the second member 120 is 180 °. When the opening angle is about 20 ° to 180 °, the convex portions 55 of the both surfaces 5a and 5b of the cam member 5 and the concave portions of the pair of friction members 3 and 4 are shown. 35 and 45 are in a non-fitted state. In this state, the cam member 5 has the convex portions 55 of both surfaces 5a and 5b in contact with the flat portions of the friction surfaces 3a and 4a of the pair of friction members 3 and 4, and the cam member 5 is brought into contact with the pair of friction members by this contact. Inclined between 3 and 4. In this inclined state, the opposite end portions of the respective convex portions 55 of the cam member 5 come into contact with the planar portions of the friction members 3 and 4 facing each other. That is, as shown in FIG. 3, the end portion 56a of the left surface 5b opposite to the convex portion 55 of the right surface 5a of the cam member 5 comes into contact with the flat surface portion of the friction surface 4a of the second friction member 4, and the cam member The end portion 56 b of the right surface 5 a opposite to the convex portion 55 of the left surface 5 b of 5 is in contact with the flat surface portion of the friction surface 3 a of the first friction member 3. And since a friction torque generate | occur | produces between the cam member 5 and a pair of friction members 3 and 4 by these contacts, the stable friction torque can be generated. In order to allow the cam member 5 to be inclined, a gap that can be inclined is provided between the shaft hole 53 of the cam member 5 and the shaft body 22 of the shaft member 2.
　カム部材５の凸部５５が摩擦部材３，４の凹部３５，４５に嵌合していない非嵌合状態において、摩擦部材３，４の摩擦面３ａ，４ａは略平行となっている。これは軸体２２を挟んだ位置の凸部５５及び端部５６ｂがカム部材５の両面５ａ，５ｂで摩擦部材３，４のそれぞれの摩擦面３ａ，４ａに接触するためである。このように摩擦部材３，４の摩擦面３ａ，４ａが略平行となっていることにより、摩擦トルクが偏在することがなくなり、安定した摩擦トルクを発生させることができる。 When the convex portion 55 of the cam member 5 is not fitted into the concave portions 35 and 45 of the friction members 3 and 4, the friction surfaces 3a and 4a of the friction members 3 and 4 are substantially parallel. This is because the convex portion 55 and the end portion 56b at the position sandwiching the shaft body 22 come into contact with the friction surfaces 3a and 4a of the friction members 3 and 4 on both surfaces 5a and 5b of the cam member 5, respectively. Thus, since the friction surfaces 3a and 4a of the friction members 3 and 4 are substantially parallel, the friction torque is not unevenly distributed, and a stable friction torque can be generated.
　このようにカム部材５が一対の摩擦部材３，４の間で傾斜することにより、カム部材５の両面５ａ，５ｂの２つの凸部５５が摩擦部材３，４と接触した状態となると共に、カム部材５における凸部５５の反対側の端部５６ａ，５６ｂが摩擦部材３，４と接触した状態となる。従って、カム部材５と一対の摩擦部材３，４とが４点での接触状態となり、摩擦部分が多くなっている。これにより安定した摩擦トルクを得ることができる。この場合、カム部材５の両面５ａ，５ｂの凸部５５を長くすることにより、２つの凸部５５及び２つの端部５６ａ，５６ｂが略三角形位置で接触するため、摩擦部材３，４の倒れを防止して平行を保つことができ、安定した摩擦トルクを得ることができる。 In this way, the cam member 5 is inclined between the pair of friction members 3 and 4, so that the two convex portions 55 of the both surfaces 5 a and 5 b of the cam member 5 are in contact with the friction members 3 and 4, The end portions 56 a and 56 b on the cam member 5 opposite to the convex portion 55 are in contact with the friction members 3 and 4. Therefore, the cam member 5 and the pair of friction members 3 and 4 are in contact with each other at four points, and the friction portions are increased. Thereby, a stable friction torque can be obtained. In this case, since the convex portions 55 of the both surfaces 5a and 5b of the cam member 5 are lengthened, the two convex portions 55 and the two end portions 56a and 56b come into contact with each other at a substantially triangular position. Can be kept parallel and stable friction torque can be obtained.
　第２部材１２０が開角度約２０°から０°に移行する間においては、カム部材５の両面５ａ，５ｂの凸部５５及びこれに対向した一対の摩擦部材３，４の対向面３ａ，４ａの凹部３５，４５は付勢手段６の付勢力により、相互に嵌合する方向に回転力が発生する。これにより吸い込み動作が生じ、第２部材１２０が自重と相俟って閉じ状態となる。 During the transition of the second member 120 from the opening angle of about 20 ° to 0 °, the convex portions 55 of the both surfaces 5a and 5b of the cam member 5 and the opposed surfaces 3a and 4a of the pair of friction members 3 and 4 opposed thereto. The recesses 35 and 45 generate a rotational force in a direction in which the recesses 35 and 45 are engaged with each other by the biasing force of the biasing means 6. As a result, a suction operation occurs, and the second member 120 is closed in combination with its own weight.
　以上の動作中でカム部材５が斜めに傾斜するときには、カム部材５と一対の摩擦部材３，４とが４点で平行接触することから、摩擦部材３，４における摩擦面３ａ，４ａは概ね平行状態を保つ。このため付勢手段６の板ばね６ａに対して傾くような偏荷重が作用しない。 When the cam member 5 is inclined obliquely during the above operation, the cam member 5 and the pair of friction members 3 and 4 are in parallel contact at four points, so that the friction surfaces 3a and 4a of the friction members 3 and 4 are generally Keep parallel. Therefore, an unbalanced load that is inclined with respect to the leaf spring 6a of the urging means 6 does not act.
　図４において、符号３６はカム部材５の右面５ａにおける端部５６ｂが第１摩擦部材３の対向面３ａを摺動する軌跡であり、図６において、符号４６はカム部材５の左面５ｂにおける端部５６ａが第２摩擦部材４の摩擦面４ａを摺動する軌跡である。かかる軌跡３６及び４６は摩擦部材３，４に形成されている凹部３５，４５よりも外周側に形成されるものであり、カム部材５の端部５６ａ，５６ｂは摩擦部材３，４の凹部３５，４５を通過することなく、摩擦部材３，４の平面部分を通過するようになっている。これにより摩擦トルクの変動を少なくすることができ、安定した摩擦トルクとすることができる。このような軌跡３６，４６は、カム部材５の凸部５５及び一対の摩擦部材３，４の凹部３５，４５をこれらの外周端に達しない長さに設定することにより形成することが可能となる。 In FIG. 4, reference numeral 36 denotes a locus in which the end portion 56 b on the right surface 5 a of the cam member 5 slides on the opposing surface 3 a of the first friction member 3. In FIG. 6, reference numeral 46 denotes an end on the left surface 5 b of the cam member 5. This is a trajectory in which the portion 56 a slides on the friction surface 4 a of the second friction member 4. The trajectories 36 and 46 are formed on the outer peripheral side of the concave portions 35 and 45 formed on the friction members 3 and 4, and the end portions 56 a and 56 b of the cam member 5 are formed on the concave portions 35 of the friction members 3 and 4. , 45 without passing through the plane portions of the friction members 3, 4. Thereby, the fluctuation | variation of a friction torque can be decreased and it can be set as the stable friction torque. Such locus | trajectories 36 and 46 can be formed by setting the convex part 55 of the cam member 5, and the recessed parts 35 and 45 of a pair of friction members 3 and 4 to the length which does not reach these outer peripheral ends. Become.
　以上のようにカム部材５が傾斜することにより第２摩擦部材４の軸方向の移動量が低減し、付勢手段６の板ばね６ａの撓みが低減する。例えば、カム部材５の外径が直径１０ｍｍ、凸部５５の位置が中心から３．５ｍｍであり、高さ（Ｈ）が０．５ｍｍ（図５参照）とした場合、板ばね６ａの撓み量（Ｗ１－Ｗ２）は０．５９ｍｍとなる。一方、カム部材２２０及び第２のカム部材３２０を直列に配置した図１６の従来装置においては、Ｗ１－Ｗ２＝２Ｈであり、１ｍｍとなる。この実施形態においては、Ｗ１－Ｗ２＝１．１８Ｈとなるからストロークを約４０％低減することができる。これにより、ヒンジ装置１が軸方向に長くなることを防止することができる。さらに、図１６の従来装置に対してストロークを低減できることから板ばね６ａの数を２／３とすることができるため、部品点数を削減することができる。 As described above, when the cam member 5 is inclined, the amount of movement of the second friction member 4 in the axial direction is reduced, and the bending of the leaf spring 6a of the biasing means 6 is reduced. For example, when the outer diameter of the cam member 5 is 10 mm, the position of the convex portion 55 is 3.5 mm from the center, and the height (H) is 0.5 mm (see FIG. 5), the amount of deflection of the leaf spring 6a (W1-W2) is 0.59 mm. On the other hand, in the conventional apparatus of FIG. 16 in which the cam member 220 and the second cam member 320 are arranged in series, W1−W2 = 2H, which is 1 mm. In this embodiment, since W1−W2 = 1.18H, the stroke can be reduced by about 40%. Thereby, it can prevent that the hinge apparatus 1 becomes long in an axial direction. Further, since the stroke can be reduced compared to the conventional apparatus of FIG. 16, the number of leaf springs 6a can be reduced to 2/3, so that the number of parts can be reduced.
　図７～図１０はカム部材５に形成される凸部５５の別の実施形態を示す。図示を省略するが、カム部材５を挟む一対の摩擦部材３，４の摩擦面には、それぞれの実施形態の凸部５５に対応した凹部３５，４５が形成されるものである。 7 to 10 show another embodiment of the convex portion 55 formed on the cam member 5. Although not shown in the drawings, concave portions 35 and 45 corresponding to the convex portions 55 of the respective embodiments are formed on the friction surfaces of the pair of friction members 3 and 4 sandwiching the cam member 5.
　図７においては、凸部５５がカム部材５の両面５ａ，５ｂのそれぞれに対し２つが形成されている。両面５ａ，５ｂの２つの凸部５５は、軸部材２の軸体２２の対称位置に設けられている。又、各面５ａ，５ｂの凸部５５は軸体２２と上下方向に直交する直線に対して平行方向に直線的に延びている。このような図７の凸部５５によっても安定した摩擦トルクを得ることができると共に、ストロークを低減することができ、部品点数を少なくすることができる。 In FIG. 7, two convex portions 55 are formed on each of both surfaces 5 a and 5 b of the cam member 5. The two convex portions 55 of the both surfaces 5a and 5b are provided at symmetrical positions of the shaft body 22 of the shaft member 2. Moreover, the convex part 55 of each surface 5a, 5b is linearly extended in the parallel direction with respect to the shaft 22 and the straight line orthogonal to an up-down direction. 7 can obtain a stable friction torque, reduce the stroke, and reduce the number of parts.
　図８はカム部材５の各面５ａ，５ｂに対し、２つの凸部５５が形成されている。両面５ａ，５ｂにおける２つの凸部５５は、軸部材２の軸体２２の対称位置に設けられると共に軸体２２と上下方向に直交する直線に対し直交方向に直線的に延びている。両面５ａ，５ｂの凸部５５はカム部材５をプレスすることにより形成されるものであり、これによりカム部材５を軽量化することができる。 In FIG. 8, two convex portions 55 are formed on each surface 5 a and 5 b of the cam member 5. The two convex portions 55 on the both surfaces 5a and 5b are provided at symmetrical positions of the shaft body 22 of the shaft member 2 and extend linearly in a direction orthogonal to the straight line perpendicular to the shaft body 22 in the vertical direction. The convex portions 55 of the both surfaces 5a and 5b are formed by pressing the cam member 5, whereby the cam member 5 can be reduced in weight.
　図９は右面５ａの凸部５５に対し、左面５ｂの凸部５５が軸体２２を中心とした対称位置に設けられることなく、対称位置からずれた位置に形成されている。両面５ａ，５ｂの凸部５５は、いずれも軸体２２と上下方向に直交する直線に対し直交方向に延びているが、左面５ｂの凸部５５は直線的に延びることなく幾分湾曲した状態で延びている。このような構造においても安定した摩擦トルクを得ることができると共に、ストロークを低減することができ、部品点数を削減することが可能となる。 In FIG. 9, the convex portion 55 of the left surface 5b is not provided at the symmetrical position with the shaft body 22 as the center, but is formed at a position shifted from the symmetrical position with respect to the convex portion 55 of the right surface 5a. The convex portions 55 of both surfaces 5a and 5b both extend in a direction orthogonal to the straight line perpendicular to the shaft body 22 and the vertical direction, but the convex portion 55 of the left surface 5b is somewhat curved without extending linearly. It extends in. Even in such a structure, a stable friction torque can be obtained, the stroke can be reduced, and the number of parts can be reduced.
　図１０はカム部材５の両面５ａ，５ｂに対し、軸体２２の対称位置となるように凸部５５が形成されている。いずれの凸部５５も軸体２２と上下方向に直交する直線上に延びて配置されている。このような構造においても、安定した摩擦トルクを得ることができると共に、ストロークを低減させることができ、部品点数を削減することが可能となる。 In FIG. 10, convex portions 55 are formed so as to be symmetrical with respect to the shaft body 22 with respect to both surfaces 5 a and 5 b of the cam member 5. All the convex portions 55 are arranged so as to extend on a straight line perpendicular to the shaft body 22 in the vertical direction. Even in such a structure, a stable friction torque can be obtained, the stroke can be reduced, and the number of parts can be reduced.
　図１１及び図１２は、本発明の別の実施形態のヒンジ装置１Ａ及び１Ｂをそれぞれ示し、上述した実施形態のヒンジ装置１と同一の部材には同一の符号を付してある。 11 and 12 show hinge devices 1A and 1B according to another embodiment of the present invention, respectively, and the same members as those of the hinge device 1 according to the above-described embodiment are denoted by the same reference numerals.
　図１１に示すヒンジ装置１Ａは、カム部材５に凹部５７を形成し、カム部材５を挟む一対の摩擦部材３，４に凸部３７，４７を形成するものであり、その他の構成はヒンジ装置１と同様である。凹部５７、凸部３７，４７はヒンジ装置１における凸部５５及び凹部３５，４５と同様に軸部材２の軸体２２を中心とした対称位置に設けられると共に、軸体２２と上下方向に直交する直線に対して直交方向に直線的に延びるように形成されている。すなわち、この実施形態のヒンジ装置１Ａにおいては、凹凸部をヒンジ装置１と反対に設けるものである。このような形態においても摩擦トルクを安定させることができ、部品点数を少なくして軸方向に長くなることのないヒンジ装置とすることができる。 A hinge device 1A shown in FIG. 11 has a cam member 5 formed with a concave portion 57 and a pair of friction members 3 and 4 sandwiching the cam member 5 with convex portions 37 and 47. Other configurations are hinge devices. Same as 1. The concave portions 57 and the convex portions 37 and 47 are provided at symmetrical positions around the shaft body 22 of the shaft member 2 as in the convex portions 55 and the concave portions 35 and 45 in the hinge device 1 and are orthogonal to the shaft body 22 in the vertical direction. It is formed so as to extend linearly in a direction orthogonal to the straight line. That is, in the hinge device 1 </ b> A of this embodiment, the uneven portion is provided opposite to the hinge device 1. Even in such a configuration, the friction torque can be stabilized, and the number of parts can be reduced, so that the hinge device does not become longer in the axial direction.
　図１２に示すヒンジ装置１Ｂは付勢手段６のばねとして複数の皿ばね６ｃを用いるものである。複数の皿ばね６ｃは表裏反転して隣接するように設けられている。この場合、付勢手段６と第２摩擦部材４との間には、仕切板１１が設けられて皿ばね６ｃが第２摩擦部材４と直接に接触しないようになっている。このような皿ばね６ｃを用いた場合においても摩擦トルクを安定させることができ、部品点数を少なくして軸方向に長くなることのないヒンジ装置とすることができる。 12 uses a plurality of disc springs 6c as springs of the urging means 6. In the hinge device 1B shown in FIG. The plurality of disc springs 6c are provided so as to be adjacent to each other by being reversed. In this case, a partition plate 11 is provided between the urging means 6 and the second friction member 4 so that the disc spring 6 c does not directly contact the second friction member 4. Even in the case where such a disc spring 6c is used, the friction torque can be stabilized, and the hinge device that does not become long in the axial direction by reducing the number of parts can be obtained.
　本発明は以上の実施形態に限定されることなく種々変形が可能である。例えば、カム部材５を第１部材１１０に連結して固定側とする一方、一対の摩擦部材３，４を第１部材１１０に連結して回転側としても良い。 The present invention is not limited to the above embodiment, and various modifications can be made. For example, the cam member 5 may be connected to the first member 110 to be the fixed side, while the pair of friction members 3 and 4 may be connected to the first member 110 to be the rotating side.
１、１Ａ、１Ｂ　ヒンジ装置
２　軸部材
３　第１摩擦部材
３ａ　摩擦面
４　第２摩擦部材
４ａ　摩擦面
５　カム部材
５ａ　右面
５ｂ　左面
６　付勢手段
２２　軸体
３５、４５、５７　凹部
３７、４７、５５　凸部
１１０　第１部材
１２０　第２部材 1, 1A, 1B Hinge device 2 Shaft member 3 First friction member 3a Friction surface 4 Second friction member 4a Friction surface 5 Cam member 5a Right surface 5b Left surface 6 Biasing means 22 Shaft bodies 35, 45, 57 Recesses 37, 47, 55 Projection 110 First Member 120 Second Member

Claims (5)

  1. 　第１部材と第２部材とを相対回転可能に連結するヒンジ装置であって、
    　一方の部材に固定される第１摩擦部材と、この第１摩擦部材に回転自在に支持されて他方の部材が固定される軸部材と、この軸部材に回転拘束されて軸方向移動可能に設けられるカム部材と、このカム部材を挟み前記第１摩擦部材に対向した状態で固定される第２摩擦部材と、前記第１摩擦部材とカム部材と第２摩擦部材とが接触する方向に付勢する付勢手段とを備え、
    　前記カム部材の両面の非同一位置に凸部もしくは凹部が形成され、前記第１摩擦部材及び第２摩擦部材の前記カム部材と対向する摩擦面に前記カム部材の凸部もしくは凹部に相互に嵌合する凸部もしくは凹部が形成され、前記カム部材は、凸部もしくは凹部が非嵌合状態のときに凸部もしくは凹部の反対側の端部が前記第１摩擦部材及び第２摩擦部材の摩擦面に接触するように傾斜することを特徴とするヒンジ装置。     A hinge device for connecting the first member and the second member so as to be relatively rotatable,
    A first friction member fixed to one member, a shaft member rotatably supported by the first friction member and the other member fixed thereto, and rotationally restrained by the shaft member so as to be movable in the axial direction Urged in a direction in which the first friction member, the cam member, and the second friction member come into contact with each other, a second friction member that is fixed in a state of being opposed to the first friction member with the cam member interposed therebetween And an urging means for
    Protrusions or recesses are formed at non-identical positions on both surfaces of the cam member, and the cam surfaces of the first friction member and the second friction member are mutually fitted in the protrusions or recesses of the cam member. A convex portion or a concave portion is formed, and when the convex portion or the concave portion is in a non-fitted state, the opposite end of the convex portion or the concave portion is the friction between the first friction member and the second friction member. A hinge device that is inclined so as to contact a surface.
  2. 　前記非嵌合状態で前記カム部材が傾斜しているとき、前記第１摩擦部材及び第２摩擦部材の摩擦面が略平行であることを特徴とする請求項１記載のヒンジ装置。 The hinge device according to claim 1, wherein when the cam member is inclined in the non-fitted state, the friction surfaces of the first friction member and the second friction member are substantially parallel.
  3. 　前記凸部もしくは凹部は、前記軸部材を中心とした対称位置に設けられていることを特徴とする請求項１又は２記載のヒンジ装置。 3. The hinge device according to claim 1, wherein the convex portion or the concave portion is provided at a symmetrical position with respect to the shaft member.
  4. 　前記凸部もしくは凹部は、前記軸部材と上下方向に直交する直線に対して直交方向又は平行方向に直線的に延びるように設けられていることを特徴とする請求項１乃至３のいずれか１項記載のヒンジ装置。 The said convex part or recessed part is provided so that it may extend linearly in an orthogonal direction or a parallel direction with respect to the straight line orthogonal to the said shaft member at an up-down direction. The hinge device according to item.
  5. 　前記凸部もしくは凹部は、前記カム部材の両面及び第１摩擦部材及び第２摩擦部材の摩擦面の外周端に達しない長さとなっていることを特徴とする請求項１乃至４のいずれか１項記載のヒンジ装置。 5. The projection according to claim 1, wherein the convex portion or the concave portion has a length that does not reach the outer peripheral ends of the friction surfaces of the cam member and the first friction member and the second friction member. The hinge device according to item.
PCT/JP2012/050641 2011-02-04 2012-01-13 Hinge device WO2012105296A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN2012800076141A CN103339392A (en) 2011-02-04 2012-01-13 Hinge device
JP2012555775A JP5598776B2 (en) 2011-02-04 2012-01-13 Hinge device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011-022696 2011-02-04
JP2011022696 2011-02-04

Publications (1)

Publication Number Publication Date
WO2012105296A1 true WO2012105296A1 (en) 2012-08-09

Family

ID=46602517

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/050641 WO2012105296A1 (en) 2011-02-04 2012-01-13 Hinge device

Country Status (3)

Country Link
JP (1) JP5598776B2 (en)
CN (1) CN103339392A (en)
WO (1) WO2012105296A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111795061A (en) * 2020-07-22 2020-10-20 大桥精密电子(上海)有限公司 Hinge and matching structure of hinge and box body

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105221560B (en) * 2015-10-13 2018-05-08 重庆晟初科技有限公司 A kind of connecting joint

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002030852A (en) * 2000-07-14 2002-01-31 Nhk Spring Co Ltd Opening/closing device
JP2005172133A (en) * 2003-12-11 2005-06-30 Mitsubishi Steel Mfg Co Ltd Biaxial hinge mechanism capable of harness wiring
JP2010175000A (en) * 2009-01-30 2010-08-12 Toyoda Gosei Co Ltd Turning device

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69112102T2 (en) * 1990-03-07 1996-04-04 Tofuji E M I Co Ltd Opening and closing mechanism.
CN2130955Y (en) * 1992-07-28 1993-04-28 陈桂榕 Pivot
JP4488490B2 (en) * 2004-01-09 2010-06-23 スガツネ工業株式会社 Hinge device
CN201696463U (en) * 2010-02-09 2011-01-05 连鋐科技股份有限公司 Concave-convex wheel structure of hub device

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002030852A (en) * 2000-07-14 2002-01-31 Nhk Spring Co Ltd Opening/closing device
JP2005172133A (en) * 2003-12-11 2005-06-30 Mitsubishi Steel Mfg Co Ltd Biaxial hinge mechanism capable of harness wiring
JP2010175000A (en) * 2009-01-30 2010-08-12 Toyoda Gosei Co Ltd Turning device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111795061A (en) * 2020-07-22 2020-10-20 大桥精密电子(上海)有限公司 Hinge and matching structure of hinge and box body
CN111795061B (en) * 2020-07-22 2023-10-13 大桥精密电子(上海)有限公司 Hinge and matching structure of hinge and box

Also Published As

Publication number Publication date
JPWO2012105296A1 (en) 2014-07-03
JP5598776B2 (en) 2014-10-01
CN103339392A (en) 2013-10-02

Similar Documents

Publication Publication Date Title
KR101880266B1 (en) Terminal apparatus
US9778704B2 (en) Biaxial hinge and terminal device using the same
US20170328102A1 (en) Triaxial Hinge and Electronic Device Using the Same
US9388617B2 (en) Hinge device
US20160216744A1 (en) Hinge and an electronic device incorporating the same
WO2011155462A1 (en) Hinge device
KR20130020791A (en) Opening/closing device
JP4298908B2 (en) Biaxial hinge having a plurality of torque generators
JPWO2012111634A1 (en) Hinge device
US10788785B2 (en) Document cover closer and office equipment having the same
JP5598776B2 (en) Hinge device
JP4397225B2 (en) Hinge device
WO2004059182A1 (en) Hinge device with temporary angle-setting function
US20130160243A1 (en) Hinge mechanism
TWM575953U (en) Bending mechanism and display device with flexible screen
JP4428667B2 (en) Cam type hinge mechanism
TWM606638U (en) Hinge structure
JP4062322B2 (en) Rotation support mechanism and portable terminal
JP2017181598A (en) Hinge and office machine having the same
TW201348611A (en) Flip mechanism and hinge assembly thereof
JP5374760B2 (en) Hinge device
JP4739429B2 (en) 2-axis hinge
US8677567B2 (en) Hinge and bracket for hinge
WO2010134211A1 (en) Hinge apparatus
JP2016037979A (en) Tilt hinge and notebook personal computer using the same

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12741565

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2012555775

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12741565

Country of ref document: EP

Kind code of ref document: A1