JP2012102797A - Hinge mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To propose a compact hinge mechanism with which a rotation object does not move downward or jump upward when the rotation object is stopped midway through the motion.SOLUTION: The hinge mechanism is formed by combining a torque limiter composed of a shaft member having a locking part and a torque generating member for generating a predetermined torque value between it and the shaft member, and a one-way clutch composed of a first cam member having a first annular cam surface, a second cam member having a second annular cam surface combined with the annular cam surface, and an elastic member for applying pressing force between the first and second annular cam surfaces.

Description

  The present invention relates to a hinge mechanism suitable for rotating an object to be rotated, such as a rear door of a vehicle body or a lid of a piano, within a predetermined angle range.

  A wide variety of hinge mechanisms are used for opening and closing mechanisms such as various doors and lids of personal computers. Many hinge mechanisms with a structure suitable for each opening / closing mechanism have been proposed, but as a simple structure, a coil spring is wound around a shaft member or an inner ring member, or another spring member is mounted, and between them, A hinge mechanism using the generated torque has been proposed (for example, see Patent Documents 1 and 2). Further, a hinge mechanism combining a hinge and a damper has been proposed as an example of a relatively heavy rear door opening / closing mechanism of the vehicle body (see, for example, Patent Documents 3 and 4).

  The hinge mechanisms according to the inventions of the aforementioned Patent Documents 1 and 2 attach a spring body to a shaft member or the like and fix a one-way clutch to generate torque generated between the shaft member or the like and the spring body. Since the unidirectionality of the directional clutch is used, the structure is simple and the number of parts is small, so it is compact and economical. It rotates idly in one rotational direction, and the desired amount of rotational torque is applied in the other direction. It is what happens.

  However, the hinge mechanism according to the inventions of Patent Documents 1 and 2 can be opened with a relatively small force when opening the rear door, such as a rear door opening / closing mechanism of a vehicle body, and the weight of the rear door when closing. Therefore, it cannot be said that it is suitable for an opening / closing mechanism that requires a large opening / closing characteristic that does not close suddenly, that is, a large rotational torque required and a characteristic that the rotational torque generated by the rotational direction differs.

  To explain this point, when the one-way clutch is composed of an inner ring member, an outer ring member, a rolling member such as a roller, and a spring member that applies a pressing force (preload) to the rolling member, When the rolling member rotates without biting between the inner ring member and the outer ring member, the inner ring member and the outer ring member are in an unlocked state and idle. In the reverse rotation direction, the rolling member bites between the inner ring member and the outer ring member, so that the inner ring member and the outer ring member are locked and cannot rotate. Since this one-way rotation operation is widely known and will not be described in further detail, it is known that a one-way clutch having such a structure causes backlash. In particular, in a one-way clutch that handles a large rotational torque, backlash may increase due to the above-described structure.

  For example, when the object to be rotated is the rear door of the vehicle body, the rear door may move slightly downward when the hand is released while the rear door is opened upward. Also, if the hand is released while the rear door of the vehicle body is closed downward, the rear door may jump up slightly at that moment. Furthermore, the hinge mechanisms according to the inventions of Patent Documents 1 and 2 are difficult to stably hold a rotating object such as various doors or lids at a specific position, and impacts are added to the rotating object. If this is done, there is a problem that the rotating object may move.

  The hinge mechanism of the invention disclosed in the above-mentioned Patent Documents 3 and 4 is built for the opening / closing mechanism of the rear door of the vehicle body, and satisfies the characteristics required for the hinge mechanism, but lacks versatility, The difficulty is that the installation is complex and requires a large installation location. In addition, since the opening / closing mechanism is not only a hinge, but also a combination of a hinge member that moves in a curved line and a damper, the opening / closing mechanism must be enlarged, and it is difficult to achieve a compact structure. It was. Further, these hinge mechanisms require an auxiliary mechanism that stably stops the rear door at a desired position at a specific position during opening and closing, and noise generated when the auxiliary mechanisms mesh with each other is also undesirable.

Japanese Patent Application Laid-Open No. 2003-042181 JP 2000-352427 A Japanese Patent Laying-Open No. 2005-088714 Japanese Patent Laid-Open No. 10-153045

  The problem to be solved by the present invention is that the conventional hinge mechanism is rotated by the backlash of the one-way clutch, particularly when applied to a hinge mechanism that rotates an object to be rotated upward or downward. At the moment when the operation of the object is stopped, the object may move slightly in the direction in which the object is rotated or may jump up in the opposite direction.

  An object of the present invention is to solve the conventional problems as described above, and is a compact hinge mechanism that rotates a rotating object upward or downward by eliminating backlash of a one-way clutch. Even when applied to the hinge mechanism, the rotating object moves downward at the moment when the upward movement of the rotating object is stopped, or the rotating object stops at the moment when the downward movement of the rotating object is stopped. This suggests a hinge mechanism that does not spring up.

  1st invention surrounds the shaft member which has a latching | locking part, the torque generation member which generate | occur | produces a predetermined torque value between the part of the shaft member, the shaft member, and the torque generation member And a first cam member having a first annular cam surface and a locking portion, and a second annular cam surface combined with the first annular cam surface. A second cam member, an elastic member for applying a pressing force between the first annular cam surface and the second annular cam surface, the first cam member and the second cam member A second housing surrounding the elastic member, and the second cam member and the elastic member, or the second housing is inserted through the shaft member extending outward from the first housing. A first central hole, and a first hole The jing and the second housing each have a mounting portion, the shaft member extending outward from the first housing is inserted into the second housing, and the locking portion of the shaft member is inserted into the first housing. A hinge mechanism is proposed in which the cam mechanism is locked to the locking portion of the cam member.

  According to a second aspect of the present invention, when a relatively reverse rotational force is applied to the first housing and the second housing, the first cam member and the second cam member are controlled according to the rotational direction. Operates as a one-way clutch that exhibits a locked state that cannot rotate relative to each other, or that exhibits a non-locked state that can rotate in a relatively reverse direction when a rotational force of a predetermined value or more is applied. The first housing rotates with respect to the shaft member when a rotational force greater than a set value is applied in a rotation direction in which the cam member and the second cam member are in a non-rotatable locked state. The hinge mechanism according to claim 1 is proposed.

  According to a third aspect of the invention, the first cam member is supported by the first housing so as to be rotatable with respect to the first housing, and the second cam member is the second housing. The second housing engages with the engaging portion of the second cam member so that it cannot move substantially in the rotational direction but moves in the length direction of the shaft member. The hinge mechanism according to claim 1 or claim 2, further comprising an engaging groove.

  According to a fourth aspect of the invention, the first annular cam surface and the second annular cam surface are respectively provided on an annular side surface of the first cam member and an annular side surface of the second cam member. 4. The concavo-convex structure formed at a constant width, which is formed with a steep slope with respect to one rotational direction and a gentle slope with respect to the other rotational direction. A hinge mechanism as described above is proposed.

  According to the present invention, the hinge mechanism is compact and has no backlash in one-way operation, and the rotating object does not move downward or jump upward when the rotating object stops operating halfway. Can be proposed.

It is a figure which shows the external appearance of the components which comprise the hinge mechanism of Embodiment 1 which concerns on this invention. It is a figure which shows the cross section of the hinge mechanism of Embodiment 1 which concerns on this invention. It is a figure which shows the external appearance of the one part component which comprises the hinge mechanism of Embodiment 1 which concerns on this invention. It is a figure for demonstrating the cam surface of the 1st cam member used for the hinge mechanism of Embodiment 1 which concerns on this invention. It is a figure for demonstrating the cam surface of the 2nd cam member used for the hinge mechanism of Embodiment 1 which concerns on this invention. It is a figure for demonstrating the cam surface of the 1st cam member of the hinge mechanism of Embodiment 1 which concerns on this invention, and a 2nd cam member. It is a figure which shows the cross section of the hinge mechanism of Embodiment 2 which concerns on this invention.

  The present invention relates to a first housing enclosing a shaft member having a locking portion and a torque generating member that generates a predetermined torque value between a part of the shaft member, and a first annular cam A first cam member having a surface, a second cam member having a second annular cam surface combined with the first annular cam surface, the first annular cam surface, and the second This is a hinge mechanism that combines a second housing that surrounds an elastic member that applies a pressing force between the annular cam surface. In addition, this invention is not limited to embodiment shown below. In the present specification and drawings, components having the same reference numerals indicate members having the same name.

[Embodiment 1]
The hinge mechanism 1 according to the first embodiment of the present invention will be described with reference to FIGS. FIG. 1 shows respective external views before the first housing 2 and the second housing 4 are combined with each other by the shaft member 3. FIG. 2 is a view showing a cross section of the hinge mechanism 1 after the first housing 2 and the second housing 4 are combined with the shaft member 3. FIG. 3 shows a combination of the first cam member 6 and the second cam member 7. FIG. 4 is a view for explaining the first annular cam surface 6 </ b> C formed on one annular side surface of the first cam member 6, and FIG. 5 shows one of the second cam members 7. It is a figure for demonstrating the 2nd annular cam surface 7C formed in the cyclic | annular side surface. FIG. 6 is a view for explaining the uneven shapes of the annular cam surfaces of both the first cam member 6 and the second cam member 7.

  As shown in FIG. 1, the outline of the hinge mechanism 1 includes a first housing 2 such as a case or a resin mold as viewed from the exterior, a shaft member 3 extending outward from the first housing 2, and a shaft member 3. It consists of the 2nd housing 4 which receives and latches. The hinge mechanism 1 is configured by inserting the shaft member 3 into the second housing 4 and locking the shaft member 3 to the components in the second housing 4. As shown in FIG. 2, a torque generating member 5 is accommodated in the first housing 2, and a first cam member 6, a second cam member 7, an elastic member 8, and a side wall are stored in the second housing 4. The member 9 is accommodated. Here, the parts including the first housing 2 and the shaft member 3 form a torque limiter, and the parts including the second housing 4 and the first and second cam members 6 and 7 form a one-way clutch. To do.

  In FIG. 2, the first housing 2 surrounds a part of the shaft member 3 and a torque generating member 5 that generates a predetermined magnitude of torque. In the first embodiment, the torque generating member 5 is a plate-like spring member that is strongly wound around a part of the shaft member 3, and is hereinafter referred to as a spring member 5. The spring member 5 may be a spring member that forms a torque generating portion that generates torque more than desired between the shaft member 3 and the spring member 5 such as a plate spring or a coil spring of various shapes. The first housing 2 is a molded body formed by resin molding a torque generating portion including a spring member 5 and a part of a shaft member 3 around which the spring member 5 is wound, or a resinous or metal formed by molding in advance. It is a sex case. Here, as shown in FIG. 2, an axis extending in the length direction of the center of the shaft member 3 is referred to as a central axis XX.

  The first housing 2 is not fixed to the shaft member 3, and when the spring member 5 rotates with respect to the shaft member 3 by applying a rotational force of a predetermined value or more to the first housing 2, the spring member Rotate with 5 That is, when a rotational force of a predetermined value or more is applied between the first housing 2 and the shaft member 3, the first housing 2 and the shaft member 3 can rotate in the opposite directions relatively. As shown in FIG. 1, the first housing 2 has two mounting holes 2A. At least one mounting hole 2A is necessary. The mounting hole 2A is used to attach to a rotating object such as a rear window of a vehicle body or a fixed object such as a vehicle body or equipment using a screw (not shown).

  The shaft member 3 is preferably a round bar made of a hard metal material. The shaft member 3 is made of a material in which a portion where the spring member 5 is wound to form a torque generating portion is not easily worn. A locking portion formed at the tip end portion of the shaft member 3 extending outward from the first housing 2 is formed in a locking hole as a locking portion of a first cam member 6 described later in the second housing 4. The locking protrusion 3A is locked (hereinafter, the locking portion of the shaft member 3 is referred to as a locking protrusion 3A, and the locking portion of the first cam member 6 is referred to as a locking hole 6B). The locking projection 3A is composed of a general D-cut, a rectangular tip, or a projection standing from a round bar-like surface of the tip, and the locking projection 3A of the shaft member 3 is in the locking hole. It is preferable to have a structure that can be inserted into and firmly locked in the locking hole, but can be inserted and removed, that is, can be inserted and removed and is temporarily locked in the locking hole. But you can.

  The second housing 4 is preferably a case made of a resin material or a metal material formed in a predetermined shape by injection molding or the like, and an end 4A on one side (right side in FIG. 2) of the second housing 4 is The other end 4B is formed with a central hole 4C (left side in FIG. 2). The central hole 4C is provided in consideration of being used to insert the shaft member 3 through the central hole 4C as in the second embodiment described later. Therefore, if the structure is not as in Embodiment 2 described later, the central hole 4C is not necessarily required, and the other side of the second housing 4 may be closed.

  As shown in FIGS. 1 and 2, the second housing 4 has three engagement grooves 4 </ b> D extending along the central axis XX at equal intervals on the inside thereof. Further, as shown in FIG. 1, the second housing 4 has two mounting holes 4E. Of course, two or more mounting holes 4E may be used. The second housing 4 is attached to a rotating object such as a fixed object such as a vehicle body or equipment or a rear window of the vehicle body, for example, with a screw (not shown) using the attachment hole 4E. A first cam member 6, a second cam member 7, an elastic member 8, and a side wall member 9 are accommodated in the second housing 4 from the open end 4A side.

  The first cam member 6 includes a cylindrical main body 6A having a locking hole 6B that receives the locking projection 3A at the distal end portion of the shaft member 3 and locks them together. The locking hole 6B has a shape that fits the locking projection 3A of the shaft member 3, can receive the locking projection 3A of the shaft member 3, and has a structure in which the locking holes 6B are firmly locked to each other. However, the locking projection 6 </ b> A of the shaft member 3 may be a locking hole 6 </ b> B that can be inserted and removed. A first annular cam surface 6C as shown in FIGS. 4 and 6 is formed on one annular side surface of the cylindrical main body 6A. The first annular cam surface 6C will be described later together with the cam surface of the second cam member 7. In the cylindrical main body 6A, the diameter (outer diameter) of the cylindrical outer surface 6Aa is larger than the diameter (inner diameter) of the inner surface 4F of the housing 4 so that the cylindrical outer surface 6Aa can rotate with respect to the inner surface 4F of the housing 4. The shape is somewhat smaller. The end surface 6D of the first cam member 6 opposite to the first annular cam surface 6C is pressed against the inner surface of the end 4B of the second housing 4 by the elastic force of the elastic member 8.

  Here, the 1st cam member 6 may have the latching protrusion part which protrudes from the center part instead of the latching hole 6B mentioned above. In this case, the shaft member 3 has a locking hole formed in the distal end surface of the shaft member in place of the locking projection 3A. The locking projections have shapes and sizes inserted into the locking holes and locked to each other.

  The second cam member 7 includes a cylindrical main body 7A having a central hole 7B having a circular cross section through which the shaft member 3 is inserted. A second annular cam surface 7C as shown in FIGS. 5 and 6 is formed on the annular side surface of the cylindrical main body 7A on the first cam member 6 side. As shown in FIGS. 3 and 5, three rotation suppression protrusions 7 </ b> Ab standing from the outer surface 7 </ b> Aa are formed on the outer surface 7 </ b> Aa of the cylindrical main body 7 </ b> A at equal intervals. The rotation restraining protrusions 7Ab are received in the engaging grooves 4D formed at equal intervals on the inner side of the second housing 4, and the second cam member is acted on by the action of the rotation inhibiting protrusions 7Ab and the engaging grooves 4D. 7 cannot move in the rotational direction, but can move in the direction of the central axis XX.

  As shown in FIG. 5, only one of the three rotation restraining protrusions 7Ab is taller than the others, and the first rotation restraining protrusion 7Ab is adapted to fit the tall rotation restraining protrusion 7Ab. Of the three engaging grooves 4D of the two housings 4, only one is a deep groove. The tall rotation restraining protrusion 7Ab and the deep groove engaging groove 4D surely position the second cam member 7 in the rotational direction of the second housing 4 and reliably restrain the rotation of the second cam 7. ing. A combined structure of the first annular cam surface 6C and the second annular cam surface 7C is indicated by a one-way clutch portion W in FIGS. The numbers of the engaging grooves 4D and the rotation suppression protrusions 7Ab are not limited to three.

  As shown in FIGS. 4 to 6, the first annular cam surface 6C and the second annular cam surface 7C are composed of irregularities that repeat in a sawtooth manner with a constant width. In FIG. 4, it is shown that the distance between the straight line 6x indicating the boundary of the unevenness and the adjacent straight line 6x are almost the same, and the widths of the sawtooth unevenness of the first annular cam surface 6C are substantially equal. Similarly, in FIG. 5, the distance between the straight line 7x indicating the boundary between the concaves and convexes and the adjacent straight line 7x are almost the same, and the widths of the saw-toothed concaves and convexes of the second annular cam surface 7C are almost equal. Indicates. The width and height of the saw-tooth irregularities of the first annular cam surface 6C and the second annular cam surface 7C are substantially the same. That is, the first annular cam surface 6C and the second annular cam surface 7C have shapes that are compatible with each other so that the cam operation can be performed in one direction.

  In FIG. 6, the first annular cam surface 6 </ b> C and the second annular cam surface 7 </ b> C arranged in an annular shape are shown in a linear structure. As shown in FIG. 6A, the first annular cam surface 6C has a gentle slope with respect to one rotational direction (the direction of the arrow A1), that is, a gentle slope 6Ca, and the other rotational direction ( It consists of a plurality of projections and depressions having a steep slope 6Cb that is steep with respect to the direction of arrow A2. Similarly, the second annular cam surface 7C also has a slope 7Ca that is gently inclined with respect to one rotational direction (arrow A1 direction), and a slope 7Cb that is steeply inclined with respect to the other rotational direction (arrow A2 direction). It consists of a plurality of irregularities.

  Although these inclination angles are not limited, when a rotational force in the arrow direction A2 opposite to the arrow A1 direction in FIG. 6 is applied between the first cam member 6 and the second cam member 7, it is abrupt. The slope 6Cb and the slope 7Cb are inclined so that the first annular cam surface 6C and the second annular cam surface 7C are engaged with each other, and the second cam member 7 is formed by the first cam member 6. It must be steep enough to prevent rotation in the arrow direction A2 in FIG. On the other hand, when a rotational force in the direction of arrow A1 in FIG. 6 is applied to the first cam member 6, the friction force generated between the gently inclined surfaces 6Ca and 7Ca is caused by the elastic force of the spring member 8 described later. The first annular cam surface 6C is non-locked with the second annular cam surface 7C and slides, the first cam member 6 is in the direction of arrow A1, and the second cam member 7 is arrowed. It is preferable that the slope be gentle enough to rotate in the A2 direction as easily as possible.

  In the combination of the first cam member 6 and the second cam member 7 shown in FIG. 3, the first cam member 6 is inclined from the inclination of the first annular cam surface 6C and the second annular cam surface 7C. When the rotational force in the direction of the arrow A1 is applied to the first cam member 6, the first cam member 6 is unlocked and rotates in the direction of the arrow A1. On the other hand, as can be seen from FIGS. 3 and 6, due to the structure of the first annular cam surface 6C and the second annular cam surface 7C, the steep slope 6Cb and the steep slope 7Cb are nectar. When there is a rotational force in the direction of the arrow A2 opposite to the direction of the arrow A1, there is no play between the first annular cam surface 6C and the second annular cam surface 7C. The first cam member 6 is locked in the arrow A2 direction, and the second cam member 7 does not move at all in the arrow A1 direction. That is, no rotation occurs in the one-way clutch portion W.

  FIG. 6B shows another shape of the first annular cam surface 6C and the second annular cam surface 7C. Both sides of the gently inclined surface 6Ca of the first annular cam surface 6C are more gently inclined or flat surfaces 6Cc and 6Cd. In addition, both sides of the gently inclined slope 7Ca of the second annular cam surface 7C are more gently inclined or flat faces 7Cc and 7Cd. As described above, the inclined surface on one side of the first annular cam surface 6C is composed of the gently inclined surface 6Ca and the surfaces 6Cc and 6Cd which are more gently inclined or flat than the inclined surface 6C, and the second annular cam surface 6C. Since the inclined surface on one side of the surface 7C is composed of the gently inclined surface 7Ca and the more gently inclined or flat surfaces 7Cc and 7Cd, when the rotational force in the direction of the arrow A1 is applied to the first cam member 6, Compared to the one shown in FIG. 6A, not only the one-way clutch W is rotated with a smaller rotational force but also the noise is small. In addition, when the rotational force in the direction of arrow A2 is applied to the second cam member 7, not only the one-way clutch portion W is rotated with a smaller rotational force than that shown in FIG. The noise is small. When the rotational force in the arrow direction A2 is applied to the first cam member 6, or when the rotational force in the arrow direction A1 is applied to the second cam member 7, it is the same as that shown in FIG. There is virtually no play.

  Returning to FIG. 2, the elastic member 8 and the side wall member 9 will be described. In the first embodiment, the elastic member 8 is formed of a coil spring having a plurality of turns, and naturally has a central hole through which the shaft member 3 is inserted. The side wall member 9 has a small-diameter portion 9A having a small outer diameter, a large-diameter portion 9B having a larger outer diameter than the small-diameter portion 9A, a press-fit portion 9C slightly protruding from the outer surface of the large-diameter portion 9B, and a central hole through which the shaft member 3 is inserted. 9D. The small-diameter portion 9A of the side wall member 9 is located between the elastic member 8 and the shaft member 3, and contacts the shaft member 3 when the elastic member 8 contracts due to the force applied to the elastic member 8 in the direction of the central axis XX. Do not work. The press-fitting portion 9 </ b> C of the side wall member 9 is press-fitted into an annular shallow groove 4 </ b> G formed inside the second housing 4.

  In a state where the press-fitting portion 9C of the side wall member 9 is press-fitted into the annular shallow groove 4G, the elastic member 8 is sandwiched between the cylindrical main body 7A of the second cam member 7 and the large-diameter portion 9B of the side wall member 9. Therefore, the second cam member 7 is pressed. That is, a pressing force is always applied to the one-way clutch portion W. In addition to the coil spring, the elastic member 8 applies a pressing force to the second cam member 7 such as an annular corrugated spring having excellent elastic force, various thin plate springs such as a C-shaped plate spring, or rubber. It only needs to be given continuously.

  Next, the operation will be described. First, as described above, the part including the first housing 2 and the shaft member 3 functions as a torque limiter, and the part including the second housing 4 and the first and second cam members 6 and 7 is a one-way clutch. Work as. Therefore, when the component consisting of the first housing 2 and the shaft member 3 is a single component, it can be used as a torque limiter. Further, the parts including the second housing 4 and the first and second cam members 6 and 7 can be used as a one-way clutch by being combined with a shaft member (not shown).

  Next, as shown in FIG. 2, the shaft member 3 is inserted from the central hole 9D of the side wall member 9, and the central hole 7B of the second cam member 7 is inserted, and the locking portion 3A of the shaft member 3 is moved to the first hole. The hinge mechanism 1 is formed by being inserted and locked in the locking portion 6B of the cam member 6. The 2nd cam member 7 and the side wall member 9 also have a role which supports the shaft member 3 rotatably. It is assumed that the first housing 2 is attached to a rotating object (not shown) and the second housing 4 is attached to a fixed object (not shown). Now, assuming that a force for rotating the first cam member 6 in the direction of arrow A1 in FIG. 3 and FIG. 6 is applied to the first housing 2, the rotational force is transmitted to the first cam member 6 through the shaft member 3. Then, the first cam member 6 tries to rotate in the arrow A1 direction. As described above, the second cam member 7 cannot rotate with respect to the second housing 4.

  The one-way clutch W between the first annular cam surface 6C and the second annular cam surface 7C is pressed by the elastic member 8, but the direction of the arrow A1 applied to the first cam member 6 6 to a certain extent, the second cam member 7 moves as the slope 6Ca of the first cam member 6 slides up the slope 7Ca of the second cam member 7 in FIG. The elastic member 8 retreats in the direction of the side wall member 9 along the central axis XX against the pressing force of the elastic member 8. By such an operation, it is possible to repeat the operation in which the gently inclined slope 6Ca of the first cam member 6 slides over the gently inclined face 7Ca of the second cam member 7 and exceeds the top of the unevenness. As described above, when the rotational force that rotates the first cam member 6 in the direction of the arrow A1 is applied to the first housing 2, the first housing 2 can be rotated in the direction of the arrow A1 with a small external rotational force. it can. That is, the rotating object can be raised upward with a force slightly larger than the moment force generated by the weight of the rotating object.

  Next, when the rotational force that rotates the first cam member 6 in the direction of the arrow A2 is applied to the first housing 2, the steeply inclined surface 6Cb of the first annular cam surface 6C and the second annular cam surface The force acting on the 7C steep slope 7Cb is substantially only in the rotational direction, and substantially no force is exerted in the central axis XX direction. Accordingly, since the force acting in the direction of the central axis XX does not exceed the pressing force of the elastic member 8, the steep slope 6Cb and the steep slope 7Cb move away from each other in the direction of the central axis XX. There is no. That is, the one-way clutch portion W rotates in an unlocked state with respect to the rotational force in the direction of arrow A1, and does not rotate in the locked state with respect to the rotational force in the direction of arrow A2. Presents.

  In the case of the one-way clutch portion W composed of the first annular cam surface 6C and the second annular cam surface 7C of the present invention, the pressing force of the elastic member 8 is applied in the direction of the central axis XX. No elastic force is applied in the rotation direction, and the steep slope 6Cb of the first cam member 6 and the steep slope 7Cb of the second cam member 7 are in close contact with each other, and the slope is gentle. 6Ca and gentle slope 7Ca are also in close contact with each other. Accordingly, no one-way backlash occurs in the one-way clutch portion W.

  That is, in the one-way clutch W, the steep slope 6Cb of the first cam member 6 and the steep slope 7Cb of the second cam member 7 are in close contact with each other, and the gentle slope 6Ca and the gentle slope 7Ca. Are stopped in close contact with each other, no backlash is generated even when the rotational force that rotates the first cam member 6 in the direction of the arrow A2 is applied to the first housing 2, and the steeply inclined surface 6Cb is steeply inclined. No movement occurs between the slope 7Cb. Therefore, the first housing 2 does not move at the initial stage when the rotational force that rotates the first cam member 6 in the direction of the arrow A2 is applied to the first housing 2. Further, even if the rotational force that rotates the first cam member 6 in the direction of the arrow A2 is removed, no movement occurs in the one-way clutch portion W, and therefore the first housing 2 does not jump up.

  When the one-way clutch portion W is in the locked state, for example, the moment force generated by the weight of the rotating object attached to the first housing 2 generates torque with the shaft member 3 in the first housing 2. Since rotation does not occur between the members 5, the rotating object does not move. However, when an external force that pushes the rotating object downward acts, the torque generated between the shaft member 3 and the torque generating member 5 is the sum of the external force and the moment force generated by the weight of the rotating object. If it exceeds, torque generating member 5 will rotate. Along with this, the first housing 2 rotates together with the torque generating member 5, and thus the rotating object rotates downward. When the external force is removed, as described above, the steep slope 6Cb of the first cam member 6 and the steep slope 7Cb of the second cam member 7 are in close contact with each other. It stops exactly at the removed position and does not cause a phenomenon of jumping up.

  Accordingly, by appropriately setting the torque generated between the shaft member 3 and the torque generating member 5, the rotating object does not move downward by an external force such as an impact, and the rotating object can be easily rotated by a relatively small force. Can be rotated downward. In the above description, the first housing 2 is attached to a rotating object (not shown) and the second housing 4 is attached to a fixed object (not shown). Conversely, the first housing 2 is fixed (not shown). The second housing 4 may be attached to a rotating object (not shown). In this case, since the operation is only reversed, the description is omitted.

[Embodiment 2]
A hinge mechanism 10 according to the second embodiment of the present invention shown in FIG. 7 includes a first housing 2, a shaft member 3, and a second housing member 4 having the same structure as that used in the hinge mechanism 1 according to the first embodiment. Consists of. The second housing 4 having the same structure as that of the one-way clutch shown in FIG. 2 is arranged 180 degrees opposite to the central axis XX direction, and the shaft member 3 extending from the first housing 2 is disposed in the second housing 4. Then, the locking portion 3A of the shaft member 3 is inserted into the locking portion 6B of the first cam member 6 and locked.

  The first cam member 6, the second cam member 7, the elastic member 8 and the side wall member 9 housed in the second housing 4 shown in FIG. The structure, operation, and operation of the one-way clutch unit composed of these are the same as those of the hinge mechanism 1 shown in FIG. The order in which the first cam member 6, the second cam member 7, the elastic member 8 and the side wall member 9 are accommodated in the second housing 4 is also the same as that of the second housing 4 of the hinge mechanism 1 shown in FIG. Since it may be exactly the same as the case, further explanation will be omitted.

  In the above description, the first cam member 6, the second cam member 7, the elastic member 8 and the side wall member 9 are configured so that they can be used in common for the hinge mechanism 1 and the hinge mechanism 10. Of course, a suitable structure may be used. Specifically, in the second embodiment, it is sufficient that the shaft member 3 can be firmly locked by the locking portion 6B of the first cam member 6, so that the second cam member 7, the elastic member 8 and The side wall member 9 is not necessarily provided with a central hole through which the shaft member 3 is inserted.

  The present invention is widely applicable to a hinge mechanism suitable for opening and closing a relatively heavy rotating object such as a rear window of a vehicle body or a lid of a piano in the vertical direction.

DESCRIPTION OF SYMBOLS 1 ... Hinge mechanism 2 ... 1st housing 3 ... Shaft member 3A ... Locking part (locking protrusion part)
4 ... 2nd housing 4A ... One end 4B ... The other end 4C ... Center hole 4D ... Engaging groove 4E ... Mounting hole 4F ... Inner surface 4G ..Shallow grooves 5 ... Torque generating member (spring member)
6 ... 1st cam member 6A ... Cylindrical main body 6Aa ... Cylindrical outer surface 6B ... Locking part (locking hole)
6C: First annular cam surface 6Ca: Slightly inclined surface 6Cb: Steeply inclined surface 6Cc, 6Cd: Slower or flat surface 6D: End surface 6x ... Straight line indicating the width of the unevenness 7... Second cam member 7 A... Cylindrical body 7 Aa... Outer surface 7 Ab. Cam surface 7Ca... Slightly inclined surface 7Cb... Steeply inclined surface 7Cc, 7Cd... Slower or flat surface 7x... Straight line indicating uneven width 8. .... Side wall member 9A ... Small diameter part 9B ... Large diameter part 9C ... Press-fit part 9D ... Center hole 10 ... Hinge mechanism W ... One-way clutch part A1, A2 ... Arrow XX ... Center axis

Claims (4)

A shaft member having a locking portion;
A torque generating member that generates a predetermined torque value with a portion of the shaft member;
A first housing that surrounds the shaft member and the torque generating member;
A first cam member having a first annular cam surface and a locking portion;
A second cam member having a second annular cam surface combined with the first annular cam surface;
An elastic member for applying a pressing force between the first annular cam surface and the second annular cam surface;
A second housing that surrounds the first cam member, the second cam member, and the elastic member;
The second cam member and the elastic member, or the second housing has a central hole through which the shaft member extending outward from the first housing is inserted.
Each of the first housing and the second housing has a mounting portion;
The shaft member extending outward from the first housing is inserted into the second housing, and the locking portion of the shaft member is locked to the locking portion of the first cam member. Hinge mechanism. When a rotational force in the opposite direction is applied to the first housing and the second housing, the first cam member and the second cam member cannot rotate with each other depending on the rotational direction. It operates as a one-way clutch that exhibits a locked state or exhibits a non-locked state that can rotate in a relatively reverse direction when a rotational force of a predetermined value or more is applied,
The first housing rotates with respect to the shaft member when a rotational force greater than a set value is applied in a rotational direction in which the first cam member and the second cam member are in a non-rotatable locked state. The hinge mechanism according to claim 1, wherein: The first cam member is supported by the first housing so as to be rotatable with respect to the first housing;
The second cam member cannot move substantially in the rotational direction with respect to the second housing, but the second housing can move in the longitudinal direction of the shaft member. The hinge mechanism according to claim 1, further comprising a locking groove that engages with a rotation-suppressing protrusion of the two cam members.   The first annular cam surface and the second annular cam surface are formed on the annular side surface of the first cam member and the annular side surface of the second cam member, respectively. The hinge mechanism according to any one of claims 1 to 3, comprising a concavo-convex structure that repeats with a constant width that is steeply inclined with respect to the rotational direction and is gently inclined with respect to the other rotational direction. .

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