WO2012105296A1

WO2012105296A1 - Hinge device

Info

Publication number: WO2012105296A1
Application number: PCT/JP2012/050641
Authority: WO
Inventors: 貴雄小林; 斎藤　誠; 森本　隆
Original assignee: 日本発條株式会社
Priority date: 2011-02-04
Filing date: 2012-01-13
Publication date: 2012-08-09
Also published as: JPWO2012105296A1; CN103339392A; JP5598776B2

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

Hinge device

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) 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.

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 °. 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.

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.

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.

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.

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.

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.

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.

Japanese Patent No. 4386864 Utility Model Registration No. 30111568 JP 2005-133759 A JP 2006-17313 A JP 2002-310129 A WO2004-27274

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.

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.

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.

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 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.

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.

Moreover, it is preferable that the said convex part or recessed part is provided in the symmetrical position centering on the said shaft member.

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.

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.

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.

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.

It is a disassembled perspective view which shows the hinge apparatus of one Embodiment of this invention. 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. 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. 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 | required of a hinge apparatus. (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.

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 °.

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.

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.

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. 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.

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.

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.

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.

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.

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.

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.

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.

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. 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.

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.

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.

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.

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.

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.

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.

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.

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.

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.

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.

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.

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.

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.

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.

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.

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.

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 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

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.
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. 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.
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. 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.