JP2008304044A - Hinge device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hinge device which is simple, can be easily downsized, and easily disables development of braking force on the way of turning a movable member in one direction. <P>SOLUTION: The hinge device 1 comprises a fixed member 2, the movable member 3 pivotally supported on the fixed member, and a braking means 4 for braking the turning speed of the movable member only when turned in one direction. The braking means 4 has an approximately cylindrical damper core 5 continuously provided on the movable member 3 in a turnable manner and inserted through a fixed member side shaft 10, and having a large-diameter inner peripheral portion 52 having a diameter slightly larger than the outer diameter of the shaft, and a coil spring 6 having a large-diameter coil portion 6a contacting the inner periphery of the large-diameter inner peripheral portion 52 and a small-diameter coil portion 6b contacting the outer periphery of the shaft 10. When the movable member 3 is turned in one direction as the coiling direction of the spring 6 together with the damper core 5, the spring 6 receives stress in the coiling direction via the large-diameter coil portion 6a from the small-diameter coil portion 6b together with the large-diameter coil portion to develop braking force. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a hinge device used when rotatably supporting various lids, toilet seats, doors, and the like on a main body, and in particular, a movable member (a member attached to a door, etc., hereinafter the same) is a fixed member (a member attached to the main body, The following relates to a hinge device having braking means for braking only when rotating in one of the forward and reverse directions.

  The hinge device rotatably supports the movable member with respect to the fixed member about the shaft as a fulcrum, and depending on the application, the movable member is urged in one direction by the urging means, or the rotational speed of the movable member is braked. There is also a brake that uses a one-way type as the braking means, and is braked only when the movable member rotates in one direction. As the latter hinge device, as disclosed in Patent Document 1, when the movable member (attached to the toilet seat) is rotated in the closing direction, the rotation is performed by the conversion means disposed in the cylinder. The piston converted into linear motion and disposed in the cylinder moves in the direction of the rotation axis of the movable member, and the air in the cylinder passes through the orifice formed in the piston from the front space to the rear space with respect to the direction of travel of the piston. While flowing in, a spring disposed between the piston and the cylinder is compressed. This air flow gives a braking force to the rotation of the movable member, and the braking force gradually increases due to the compression action of the spring, whereby the movable member is closed gently. When the movable member is rotated in the opening direction, the air in the cylinder flows out through the through hole formed in the orifice and the piston, and the spring is restored by its urging force, so that the braking force is expressed. Not. Patent Document 2 has a similar configuration.

JP-A-2-274216 Japanese Patent No. 2759828

  In the above-described conventional apparatus, the converting means for converting the rotational motion of the movable member into the linear motion, and the braking force is applied to the rotational motion of the movable member or the braking force is increased with the rotational motion of the movable member. It consists of a cylinder, a piston, and a spring. For this reason, in the conventional apparatus, the structure is complicated and expensive, and a space in consideration of the movement of the piston is also required, so that it tends to be large. Accordingly, the object of the present invention is to solve the above-mentioned problems, to easily achieve a reduction in size and to easily make it impossible to express the braking force during the rotation of the movable member in one direction. There is in making it possible.

In order to achieve the above object, the invention of claim 1 is directed to a fixed member, a movable member pivotally supported by the fixed member, and the movable member rotating in one of the forward and reverse directions. And a braking device that brakes the rotational speed of the movable member only when the movable member is pivotally connected to the movable member so as to be integrally rotatable. A substantially cylindrical damper core that is inserted into the shaft and forms a large inner peripheral portion that is slightly larger than the outer diameter of the shaft, and a large diameter that is in contact with the inner periphery of the large inner peripheral portion of the damper core A coil spring, and a coil spring integrally forming a small-diameter coil section that contacts the outer periphery of the shaft;
When the movable member is rotated together with the damper core in one direction which is a coil winding direction of the coil spring, the coil spring is moved to the small diameter coil portion together with the large diameter coil portion via the large diameter coil portion. It is characterized in that a braking force is developed by receiving stress in the coil winding direction.

The above hinge device is more preferably embodied as in claims 2 to 4.
(Claim 2) A clutch mechanism for connecting and disconnecting the movable member and the damper core is provided, and the clutch mechanism is configured so that the movable member and the damper core are in the middle of being rotated in one direction. By switching from contact to disconnected state, the braking force by the coil spring cannot be expressed.
(Claim 3) The clutch mechanism includes a clutch spring that connects one end side of the damper core and a facing portion on the movable member side so as to be able to contact and disconnect, and the other end side of the damper core and the movable member. And a cam mechanism that is interposed between the opposite facing portion and enables the damper core to return to the reference position.
(Claim 4) It is the structure which is provided between the said fixed member and the said movable member, and has the urging means which urges | biases the said movable member with respect to the said fixed member to one direction.
(Claim 5) The urging member comprises a coil spring disposed with a gap around the outer periphery of the damper core.

  In the first aspect of the invention, the braking means comprises a cylindrical damper core that is inserted through the pivot shaft on the fixed member side, and a coil spring disposed between the shaft and the damper core. There are few, it is easy and it is easy to plan downsizing. When the movable member is rotated in one direction together with the damper core, the braking means is controlled by the coil spring receiving stress in the coil winding direction along with the large-diameter coil portion and the small-diameter coil portion via the large-diameter coil portion. On the contrary, when the movable member is rotated in the other direction together with the damper core, the coil spring is unwound in the small coil portion together with the large coil portion via the large coil portion. The braking force cannot be expressed by receiving the stress.

  In the invention of claim 2, the stress from the damper core with respect to the coil spring is applied by switching the movable member and the damper core from the contact state to the disconnected state by the clutch mechanism while the movable member is rotated in one direction. Without it, the braking force cannot be expressed. For this reason, as the braking means, the braking force is a one-way type, and braking is not performed in the middle of one direction, whereby the braking range can be set finely and the degree of freedom in design can be expanded.

  According to a third aspect of the present invention, when the braking means in the second aspect causes the movable member and the damper core to be disconnected by the clutch mechanism, the damper core is arbitrarily rotated, and the clutch mechanism is again switched to the contact state with the movable member. The cam mechanism corrects that the position of contact / disconnection is out of order so that braking and non-braking can always be switched at a constant angle in rotation in one direction.

  In the invention of claim 4, as the hinge device having the braking means and the urging means, the movable member is urged in one direction (in the embodiment, the closing direction of the door) by the urging means, and in one direction by the urging force. It is ideal for applications that rotate. In the invention of claim 5, since the urging means of claim 4 is a coil spring arranged outside the damper core, it is possible to maintain the size reduction even if the urging means is added.

  The best mode of the present invention will be described with reference to the drawings. In the drawings, FIGS. 1 to 8 show a hinge device of an embodiment, and FIG. 9 shows a modified example in which the hinge device is simplified. In the following description, the hinge structure, the braking means and the operation thereof, the clutch mechanism and the operation thereof, the cam mechanism and the operation thereof, and a modification will be described in detail.

(Hinge structure) The hinge device 1 of the form example includes, for example, a movable body (a door, a lid, a toilet seat, etc., and will be described assuming a door for a locker in the following example). In the following example, description will be made assuming that the locker body is assumed to be openable and closable, and it is pivotally supported by the fixing member 2 and the fixing member 2. The movable member 3 and the braking means 4 for braking the rotational speed of the movable member only when the movable member 3 is rotated in one of the forward and reverse directions, the clutch mechanism 14, the cam mechanism 18, and the biasing force. And a coil spring 19 as means. In the hinge device 1 of the present invention, the clutch mechanism 14, the cam mechanism 18, and the coil spring 19 can be omitted. The clutch mechanism 14, the cam mechanism 18, and the coil spring 19 function independently of each other. It is.

  Here, the fixed member 2 and the movable member 3 are rotatably connected through a pivot shaft 10 on the fixed member side. For example, the side plate on which the fixed member 2 borders the opening of the main body. In the state where the movable member 3 is attached to the corresponding side portion of the door that opens and closes the main body side opening, the closed position where the door closes the main body side opening and the opening is exposed or opened. Any relationship may be used as long as the rotation can be switched to the open position.

  That is, the fixing member 2 is a bracket or a metal fitting attached to a corresponding portion of the main body, and the schematic shape is a U-shape obtained by bending both side portions 21 and 22 of the intermediate plate portion 20 in the same direction, and each side portion. A mounting portion 23 is formed so as to protrude horizontally from the outer lower side of 21 and 22. As shown in FIG. 6, the intermediate plate portion 20 is between the side wall 21 and the side wall 22, and has a window portion 24 in which the front and rear intermediate portions are cut out, and a thin side portion 20 a on the front side that partitions the window portion 24. And a wide side portion 20b on the rear side. The side portion 20a has a restriction projection 25 provided on the front end surface near the side portion 21 and bent upward through a pair of slits, and a locking recess provided on the rear end surface near the side portion 22. 26. Further, mounting holes 27a and 27b are provided in the side portion 20b and the mounting portions 23, respectively. As shown in FIG. 4, through holes 28 and 29 are provided on the side line 21 and the side part 22 on the coaxial line. The through hole 28 is a non-circular hole in which the engaged portion 12 of the shaft 10 is engaged so as not to rotate. The through hole 29 may be any hole that allows the tip of the shaft 10 to be inserted therethrough.

  The movable member 3 is, for example, a bracket or a metal fitting attached to a corresponding portion of a door, and the rough shape is an inverted L-shaped plate width that is inserted into the fixed member-side window portion 24 with a margin, and an L-shaped horizontal portion. 30 is disposed between the side portion 21 and the side portion 22 on the fixing member side, and an L-shaped vertical portion 31 is inserted through the window portion 24. As shown in FIG. 4, the horizontal portion 30 has a rectangular hole portion 32 formed on the front end side, and side portions 33 and 34 formed to protrude downward from both sides. The hole 32 is a viewing hole for the coil spring 19 described later, but may be omitted. The side portion 33 and the side portion 34 are provided with through holes 35 and 36 on the same line. The through hole 35 faces the through hole 28 and is a non-circular hole similar to the through hole 28. The through hole 36 is a cam mounting hole that is opposed to the through hole 29 and is slightly larger than the through hole 29 and is non-circular. A plurality of attachment holes 31 a are provided in the vertical portion 31.

  As shown in FIG. 4, the shaft 10 includes a head portion 11 that is in contact with the side portion 21, a non-circular engaged portion 12 that is non-rotatably engaged with the through hole 28 of the side portion 21, and a side portion 22. And a circular shaft portion 13 inserted through the through-hole 29. And in the operation which assembles each member mentioned below, shaft 10 inserted movable member side perpendicular part 31 below fixed member side window part 24, and arranged horizontal part 30 between side part 21 and side part 22. From the state, the shaft portion 13 is attached to the through hole 28 of the side portion 21, the hole of the damper connect 38, the cylinder of the damper core 5, the center insertion hole of the one side cam 16 attached to the damper core 5, and the through hole 36. The other side cam 17 is inserted into the center insertion hole and the through hole 29 of the side portion 22, the engaged portion 12 is engaged with the through hole 28, and the tip of the shaft portion 13 inserted through the through hole 29 is By being prevented from being removed by a retaining member (not shown) or the like, the movable member 3 is rotatably supported with respect to the fixed member 2 with the shaft portion 13 as a fulcrum. Reference numeral 7 denotes a washer interposed between the side portion 22 of the fixed member 2 and the side portion 34 of the movable member 3. The washer 7 can be omitted.

  In the above assembly operation, the coil spring 19 is disposed between the side portion 33 and the side portion 34 in advance. One end 19a of the coil spring 19 is locked to the inner surface of the movable member side horizontal portion 30, and the other end 19b is locked to the concave portion 26 on the fixed member side while exerting an urging force. Therefore, as shown in FIG. 3, the hinge device 1 is closed by the biasing force of the coil spring 19 in a state where the movable member 3 is pivotally supported about the shaft 10 with respect to the fixed member 2. And is rotated from the closed to the open direction against the biasing force.

  In the above hinge device 1, in association with the shaft 10, braking means 4 for braking only when the movable member 3 is rotated in one direction, and braking means in the middle of the movable member 3 being rotated in one direction. 4 is incorporated into the clutch mechanism 14 that disables the braking force 4 and an adjustment or correction cam mechanism 18 that keeps the clutch mechanism 14 normal.

(Braking means and its operation) The braking means 4 has a substantially cylindrical damper core 5 and a coil spring 6 integrally formed with a large-diameter coil portion 6a and a small-diameter coil portion 6b. Among these, the damper core 5 is continuously connected to the movable member 3 side via a damper connect 38 (described later) so as to be integrally rotatable, and a small-diameter outer peripheral portion 50 having an outer periphery formed on one end side and an end surface thereof. It has a horizontal groove-shaped locking groove 51 provided in a part, and has a large-diameter inner peripheral portion 52 whose inner periphery is slightly larger than the outer diameter of the shaft portion 13 except for one end side. The coil spring 6 has a rectangular wire rod cross section, a coil diameter in which the large-diameter coil portion 6 a is in contact with the inner peripheral surface of the large-diameter inner peripheral portion 52, and a coil diameter in which the small-diameter coil portion 6 b is in contact with the shaft-side shaft portion 13. Has been.

  In the braking means 4 described above, the movable member 3 and the damper core 5 and the coil winding direction of the coil spring 6 are arranged in one direction (for example, a door (not shown in FIG. 8 is opened to closed by the biasing force of the coil spring 19)). The coil spring 6 receives a stress in the coil winding direction through the large-diameter coil portion 6a and the small-diameter coil portion 6b via the large-diameter coil portion 6a, and develops a braking force. When the coil core 6 is unrolled with the damper core 5 in the other direction (for example, a door (not shown in FIG. 8) is rotated in the open direction by the biasing force of the coil spring 19), the coil spring 6 is configured to receive a stress in the direction of unwinding the small-diameter coil portion 6b together with the large-diameter coil portion 6a via the large-diameter coil portion 6a, and no braking force is generated.

  In other words, when the movable member 3 is rotated together with the damper core 5 in one direction which is the coil winding direction of the coil spring 6, the large-diameter coil portion 6a receives the stress in the coil winding direction and has a large diameter inside the damper core. The peripheral coil 52 is idling and the small-diameter coil section 6b receives a stress in the coil winding direction to increase the winding force with respect to the shaft side shaft section 13 to be in a locked state, thereby generating a braking force. When the movable member 3 is rotated in the other direction, the large-diameter coil portion 6a receives the stress in the coil unwinding direction and is locked to the damper core side large-diameter inner peripheral portion 52. The part 6b receives a stress in the direction of unwinding the coil and is idled with respect to the shaft side shaft part 13, thereby making it impossible to develop the braking force.

  By the way, the above braking mode is applied as an application example when the fixed member 2 is attached to the main body side such as a cocker, the movable member 3 is attached to the door, and the door is biased in the direction of closing the opening of the main body. It becomes as follows. That is, in the hinge device 1 having the braking means 4 and the spring member 19, the braking means 4 does not work when the door is rotated against the biasing force in the opening direction from the closed position, and the door is in the closed position from the open position. When it is rotated by the biasing force, it is braked by the braking means 4 so as to be rotated slowly. The spring member 19 is omitted, for example, in a usage mode in which a door or a toilet seat (a member attached to the movable member) is rotated by its own weight from an open position to a closed position. In that case, when the door or toilet seat is rotated from its open position to its closed position by its own weight, it is slowly rotated by the braking means 4.

(Clutch mechanism and its operation) The clutch mechanism 14 connects the damper connect 38 fixed to the side portion 33 on the movable member side, and the damper connect 38 and the small-diameter outer peripheral portion 50 of the damper core 5 so as to be able to contact and disconnect. The clutch spring 15. That is, the damper connect 38 is a shaft hole through which the inner periphery is rotatably inserted through the shaft portion 13, and the outer periphery is a non-circular engaged portion 38 a that is non-rotatably engaged with the through hole 35 of the side portion 33. An outer peripheral portion having the same diameter as that of the small-diameter outer peripheral portion 50 of the damper core 5 is integrally formed. The clutch spring 15 has a rectangular wire cross section, and is wound around the outer periphery of the damper core side small outer peripheral portion 50 and the damper connect side outer peripheral portion, and the coil one end 15a is engaged with the engaging groove 51 on the damper core side. The other end 15b of the coil is bent so that it can come into contact with the restricting projection 26 on the fixing member side. The damper connect 38 may be formed integrally with the movable member 3.

  In the clutch mechanism 14 described above, as shown in FIG. 6, the movable member 3 is rotated in one direction, that is, while being rotated from the open position to the closed position in FIG. 6B, until the angle indicated by the imaginary line in FIG. When rotated, the other end 15b of the clutch spring hits the restricting protrusion 25 on the fixed member side, and when it is further rotated in the same direction, the winding of the clutch spring 15 around the damper connect 38 is released. The fixed damper connect 38 and the damper core 5 are switched from the contact state to the disconnected state so that the braking force cannot be expressed. For this reason, in this hinge apparatus 1, the braking means 4 is a one-way type, and the clutch mechanism 14 is not braked in the middle of one direction, so that the braking range can be set finely.

  By the way, when the above-described clutch mode is used as an application example, the above-described fixing member 2 is attached to the main body side such as a cocker, the movable member 3 is attached to the door, and the door is biased in the direction of closing the opening of the main body. When applied, it becomes as follows. That is, in the hinge device 1 having the braking means 4, the spring member 19, and the clutch mechanism 14, the clutch is switched from disengagement to contact and braking when the door is rotated against the biasing force from the closed direction to the open direction. When the means 4 does not work and the door is rotated from the open position to the closed position by the urging force, the brake means 4 brakes and slowly rotates during the clutch engagement, and then the imaginary line in FIG. Is turned to the clutch disengagement, and thereafter it is quickly turned by the urging force of the spring member 19 to reach the closed position. This advantage is obtained when, for example, the door is surely switched to the normal closed position by a strong biasing force at the final stage, or the detection sensor detects whether the door is switched to the closed position. A G sensor or a pressure sensor can be used as a detection sensor.

  The braking means 4 described above, when the movable member 3 and the damper core 5 are disconnected from the contact state by the clutch mechanism 14, the damper core 5 is arbitrarily rotated, and the movable member 3 and the damper core are again rotated by the clutch mechanism 14. There is a possibility that the position of contact / disconnection when 5 is switched to the contact / disconnection state is out of order. For this reason, the hinge device 1 described above has the next cam mechanism 18 together with the clutch mechanism 14.

(Cam mechanism and its operation) As shown in FIGS. 4 and 5, the cam mechanism 18 includes a cam 16 mounted on the large-diameter inner peripheral portion 52, which is the other end of the damper core 5, and a side portion 34 of the movable member. And a cam 17 mounted in a through-hole 36 provided in the. The cam 16 and the cam 17 have a central insertion hole, a pair of convex portions 16a or a pair of convex portions 17b provided on end surfaces facing each other, and an attachment portion 16b or an attachment portion 17b. The cam 16 is engaged and fixed to the large-diameter inner peripheral portion 52 of the damper core 5 via the attachment portion 16b. The cam 17 is engaged and fixed to the through hole 36 of the side portion 34 via the mounting portion 17b. Moreover, as the hinge apparatus 1, the convex part 16a and the convex part 17a can contact | abut in the state which the shaft side axial part 13 inserted rotatably the above-mentioned insertion hole of each cam 6 and 7. As shown in FIG.

  That is, in the hinge device 1 described above, when the movable member 3 is released from the open position or the half-open state, the movable member 3 is rotated in the closing direction by the biasing force of the coil spring 19. The brake is braked to a little before (in this example, the angle a shown in FIG. 7A, that is, about 10 degrees before the closed position of the door) and slowly rotated. Thereafter, as described above, the brake mechanism cannot be braked by switching from contact to disconnection of the clutch mechanism 14 and is rapidly rotated to the closed position by the urging force of the coil spring 19.

  In that case, the cam mechanism 18 is configured such that the convex portion 17a of the cam 17 and the cam 16 are moved until the movable member 3 reaches the angle indicated by the imaginary line in FIG. 7A from the open position or the half-open state in FIG. It rotates integrally with the convex portion 16a in contact. When the movable member 3 reaches the angle indicated by the imaginary line in FIG. 7A, the clutch mechanism 14 is disconnected from the clutch engagement, and the damper core 5 is not rotated in conjunction with the movable member 3. Therefore, until the movable member 3 reaches the final closed position from the angle indicated by the imaginary line (a), only the cam 17 is rotated, that is, the angle a is independently rotated. When the movable member 3 is rotated again from the closed position to the opening direction against the biasing force of the coil spring 19, the cam mechanism 18 is configured such that the convex portion 7 a of the cam 17 is the convex portion of the damper core side cam 16. When the damper core 5 moves integrally with the cam 16 when it hits 16a, it returns to the reference or initial position via the cam 17 even if the damper core 5 moves in the clutch disengaged state. The braking by 4 (expressing braking force) and non-braking (making braking force unusable) are always switched at a constant angle.

(Modification) FIG. 9 is an example in which the above hinge device is simplified, that is, the clutch mechanism and the cam mechanism are omitted. In addition, the same code | symbol is attached | subjected to the same member and site | part on drawing. That is, the hinge device 1A is modified in the following points compared to the hinge device 1 because the clutch mechanism 14 and the cam mechanism 18 are omitted.

(1) The damper core 5 </ b> A has one end 53 engaged with and fixed to the through hole 35 of the side portion 33 in the movable member 3 so as not to rotate, and the other end of the damper core 5 </ b> A in the movable member 3 via the connecting cylinder 8 fixed. This is different from the above-described damper core 5 in that the through hole 36 of the side portion 34 is engaged and fixed in a non-rotatable manner and the large-diameter inner peripheral portion 52 is formed long.
(2) The coil spring 6A is formed so that all dimensions (large-diameter coil portion 6a and small-diameter coil portion 6b) are longer than the coil spring 6 described above according to the length of the large-diameter inner peripheral portion 52.
(3) When the movable member 3 is rotated in one direction which is the coil winding direction of the coil spring 6 together with the damper core 5 (for example, the door is opened to the closed direction by the biasing force of the coil spring 19). The coil spring 6 receives the stress in the coil winding direction from the large-diameter coil portion 6a and the small-diameter coil portion 6b via the large-diameter coil portion 6a so as to develop a braking force and rotate slowly to the final closed position. So that

  In the above hinge device, the example in which the movable member brakes the rotation speed when the movable member rotates from the open position to the closed position as the braking means has been described. However, the present invention is not limited thereto, and the movable member is the door or the like. You may make it brake when rotating from a closed to an open position. The same applies to the clutch mechanism. Applications are not limited to doors and toilet seats, and can be used for various folding structures.

It is a schematic external view which shows the hinge apparatus of invention form. (A) is the top view of the said hinge apparatus, (b) is the figure seen from the A direction of (a). (A) is the left view of the said hinge apparatus, (b) is a right view. FIG. 3 is a cross-sectional view taken along line B-B in FIG. It is a figure which shows typically the cam mechanism of the said hinge apparatus. (A) And (b) is a block diagram in the closed position of the movable member shown corresponding to CC sectional view taken on the line of FIG.2 (b), and an open position. (A) And (b) is a block diagram in the closed position and open position of a movable member shown corresponding to DD sectional view taken on the line of FIG.2 (b). (A) And (b) is typical sectional drawing which shows the relationship between the damper core shown corresponding to the EE line of FIG.2 (b), and a FF line arrow sectional drawing, a coil spring, and a shaft. (A) And (b) is a figure which shows the modification of the said hinge apparatus corresponding to Fig.2 (a) and FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,1A ... Hinge apparatus 2 ... Fixing member (20 is an intermediate | middle board part, 21 and 22 are side parts, 24 is a window part, 26 is a control protrusion)
3 ... movable member (30 is a horizontal part, 31 is a vertical part, 33 and 34 are side parts)
4, 4A: Braking means 5, 5A: Damper core (50 is a small-diameter outer peripheral portion, 51 is a locking groove, 52 is a large-diameter inner peripheral portion)
6, 6A ... Coil spring (6a is a large diameter coil portion, 6b is a small diameter coil portion)
10 ... Shaft (11 is head, 12 is engaged portion, 13 is shaft)
14 ... Clutch mechanism (38 is damper connect)
15 ... Clutch spring (15a is one end, 15b is the other end)
18 ... Cam mechanism (16 and 17 are cams, 16a and 17a are convex portions)
19: Coil spring (biasing means, 19a is one end, 19b is the other end)

Claims (5)

A fixed member, a movable member pivotally supported by the fixed member, and braking for braking the rotational speed of the movable member only when the movable member is rotated in one of the forward and reverse directions. A hinge device comprising:
The braking means is connected to the movable member so as to be rotatable integrally therewith, inserts a pivot shaft on the fixed member side, and forms a large inner peripheral portion that is slightly larger than the outer diameter of the shaft. A substantially cylindrical damper core, a large-diameter coil portion that contacts the inner periphery of the large-diameter inner peripheral portion of the damper core, and a coil spring that integrally forms a small-diameter coil portion that contacts the outer periphery of the shaft Have
When the movable member is rotated together with the damper core in one direction which is a coil winding direction of the coil spring, the coil spring is moved to the small diameter coil portion together with the large diameter coil portion via the large diameter coil portion. A hinge device characterized in that a braking force is developed in response to stress in a coil winding direction.   A clutch mechanism for connecting / disconnecting the movable member and the damper core, and the clutch mechanism disconnecting the movable member and the damper core from contact while the movable member is rotated in one direction; 2. The hinge device according to claim 1, wherein the braking force by the coil spring cannot be expressed by switching to.   The clutch mechanism includes a clutch spring that connects the one end side of the damper core and the facing portion on the movable member side so as to be able to contact and disconnect, and the other end side of the damper core and the facing portion on the movable member side. The hinge device according to claim 2, further comprising a cam mechanism that is interposed between the damper core and the damper core so that the damper core can be returned to a reference position.   4. An urging means provided between the fixed member and the movable member and urging the movable member in one direction with respect to the fixed member. The hinge apparatus in any one of.   The hinge device according to claim 4, wherein the urging means includes a coil spring disposed with a gap around the outer periphery of the damper core.

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