JP2013002482A - Hinge device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hinge device that achieves a diameter reduction in a rotation space, and eliminates the need for using a high-accuracy component.SOLUTION: In a hinge device 30, a first member 20 and a second member are mounted so as to be relatively turnable, and turning torque thereof is varied in accordance with a turning angle. The hinge device 30 includes: the first member 20; a shaft 22 the one end 20a of which is mounted on the first member 20 so as to be turnable and the other end 22b of which is fixed to the second member; a first cam 28 fixed to the first member 20; a second cam 32 which is formed so that projections and recesses are engaged with the first cam 28, is fixed to the shaft 22 so as to be turnable with the shaft 22, and has a diameter equal to that of the first cam 28; and a plurality of coned disc springs 34, 36 which are disposed while penetrating the shaft 22 so as to bring the second cam 32 into pressure-contact with the first cam and have a diameter equal to that of the first cam 28 and the second cam 34. The respective coned disc springs 34, 36 include the first coned disc spring 34 which is deformed with low pressure, and the second coned disc spring 36 which is deformed with high pressure.

Description

  The present invention relates to a hinge device provided so that torque at the time of rotation changes depending on a rotation angle.

In passenger cars and other moving means, the display device may be arranged in the vehicle. For example, a display device for a passenger car is often arranged on a ceiling surface or the like.
As shown in FIG. 10, when the user does not view the video, the display device is housed in the ceiling and closed, and when the user views the video, the display device is rotated around a rotation shaft provided so as to extend in the horizontal direction. It can be opened and rotated around the rotation axis until it is easy to see.

A hinge device that requires the following operations is adopted as the rotation shaft of such a display device.
First, until the display device is rotated from the closed state to about 30 °, if the fixing means that fixes the display device to the ceiling surface is released, the torque may be extremely weak enough to rotate by its own weight. . This is because if the display device is opened to about 30 °, the user can adjust it by hand.
Next, until the display device is rotated to about 90 °, a weak torque that can be easily rotated by hand is required. If the angle is less than 90 °, the display is difficult to see. Therefore, it is unlikely that the user can adjust the fine angle between 90 ° and 90 °.

  Next, a high torque is required until the display device is rotated from about 90 ° to about 120 °. The angle of the display device when the user actually watches is assumed to be within this range, and after the user rotates it to an angle that is easy for the user to see, the user can rotate the angle so that the angle does not change due to vibration in the vehicle. This is because it is required to stop at the moved angle.

As described above, as a hinge device in which the torque changes depending on the rotation angle, a configuration as shown in Patent Document 1 is conventionally known.
As shown in FIG. 11, according to the hinge device described in Patent Document 1, the shaft member 4 is rotatably attached to the base member 2, and the shaft member 4 has the arm portion 5 </ b> A. The member 5 is attached so as to rotate integrally with the shaft member 4. The braking member 5 is pressed against the base member 2 by a disc spring 6.
The disc spring 6 is fixed to the shaft member 4 by a flat washer 7 and a nut 8.

The arm portion 5A of the braking member 5 is formed with a projection 9 that slides in an arc-shaped groove 11 formed on the surface of the base member 2.
A recess 10 into which the protrusion 9 can enter is also formed on the arc concentric with the arc-shaped groove 11 of the base member 2.

In such a hinge device, when the shaft member 4 is rotated, the projection 9 of the braking member 5 has a low torque when moving in the groove 11, and the projection 9 is grooved by the rotation of the shaft member 4. When it comes out of 11 and is in contact with the normal surface of the base member 2, the torque is high.
Further, when the protrusion 9 of the braking member 5 enters the recess 10 and exits from the recess 10, a click feeling can be generated by the resistance force at that time.

JP 2003-56547 A

In the conventional hinge device, a projection is formed on the arm portion of the braking member, and the torque is changed by the projection and the surface shape of the base member.
However, according to such a configuration, the base member and the braking member have a large diameter as compared with a disc spring or a flat washer that stops the disc spring.
Further, in the conventional hinge device, it is necessary to use high-precision parts such as a braking member. When high-precision parts are used, there is a problem that the cost is high and manufacturing is troublesome.

  Accordingly, the present invention is made to solve the above-described problems, and an object of the present invention is to provide a hinge device that can reduce the diameter of the rotation space and does not require the use of high-precision parts.

According to the hinge device according to the present invention, in the hinge device in which the first member and the second member are mounted so as to be relatively rotatable, and the rotation torque varies depending on the rotation angle, An end portion is fixed to the second member, a shaft portion whose one end portion is rotatably attached to the first member, a first cam fixed to the first member, and the first cam and the unevenness mesh with each other. A second cam having the same diameter as the first cam, fixed to the shaft portion and rotatable with the shaft portion, and penetrating the shaft portion so as to press the second cam against the first cam. And a plurality of disc springs having the same diameter as the first cam and the second cam, each disc spring being a first disc spring that is deformed at a low pressure, and a second disc spring that is deformed at a high pressure. And a disc spring.
By adopting this configuration, it is possible to configure a hinge device in which the rotation torque changes depending on the rotation angle by using a plurality of disc springs that are deformed by different pressures (thicknesses are different). Therefore, the rotation space can be reduced without requiring a large space as in the conventional hinge device.

In addition, when the irregularities of the first cam and the second cam are just in place, the first disc spring that is deformed at a low pressure among the disc springs is deformed and a low load is applied to the second cam. Yes. That is, in this state, the rotation is performed with a low rotation torque.
Further, when the shaft portion is further rotated so that the convex portion formed on one of the concave and convex portions of the first cam and the second cam rides on a place other than the concave portion formed on the other, the interval between the first cam and the second cam is increased. In order to spread, each disc spring is pressed by the second cam, and the first disc spring that is deformed with a low pressure is compressed to be in the same state as the flat washer. At this time, the second disc spring that is deformed by a high pressure is pressed from the second cam and deformed, and a high load can be applied to the second cam. For this reason, if the convex part formed in either of the unevenness | corrugations of a 1st cam and a 2nd cam rides on locations other than the recessed part formed in the other, a high torque will be needed at the time of rotation.
In this way, the hinge device of the present invention can change the rotation torque depending on the rotation angle without using high-precision components.

The first cam and the second cam have a recess formed in one of them, and a protrusion that can enter the recess is formed on the other, and is a side wall of the recess, from the recess to the protrusion. The side from which the protrusion is separated may be formed in a tapered shape so that the convex portion is gradually separated.
According to such a configuration, since the pressing force by the disc spring gradually increases by climbing on the portion where the convex portion is formed in a tapered shape, the rotation torque is changed when switching from low torque to high torque. Can be raised gradually without raising it rapidly.

Further, one first disc spring and two second disc springs may be provided.
In this way, a desired torque can be obtained by adjusting the number of disc springs in accordance with the torque required for rotation.

  According to the hinge device according to the present invention, the rotation space can be reduced without requiring a large space as in the conventional hinge device, and high-precision parts need not be used.

It is a perspective view which shows the external appearance structure of a hinge apparatus. It is an exploded view of the hinge apparatus of FIG. It is explanatory drawing which looked at the arrangement | positioning of each cam part and each disc spring from the side surface. It is explanatory drawing explaining the condition in case the convex part of a 2nd cam enters into the recessed part of a 1st cam, and rotates with a low torque. It is explanatory drawing which shows the place where the convex part of a 2nd cam rides on a taper surface, and a torque becomes high gradually. It is explanatory drawing which shows the place where the convex part of a 2nd cam slips out from the recessed part of a 1st cam, and rotates with a high torque. It is a graph which shows the relationship between the deflection amount of a spring, and a spring load in the disk spring (low load disk spring) which deform | transforms with a low pressure. It is a graph which shows the relationship between the deflection amount of a spring, and a spring load in the disk spring (high load disk spring) which deform | transforms with a high pressure. The relationship between the amount of spring deflection and the spring load is shown when a disc spring (low load disc spring) that deforms at a low pressure and a disc spring (high load disc spring) that deforms at a high pressure are stacked as in this embodiment. It is a graph. It is explanatory drawing which looked at the display apparatus for passenger cars from the side. It is explanatory drawing of the hinge apparatus which made rotation torque change with the conventional rotation angles.

An embodiment of a hinge device according to the present invention will be described with reference to the drawings.
FIG. 1 shows an external configuration of the hinge device, and FIG. 2 shows an exploded view of the hinge device of FIG.
The hinge device 30 has a configuration in which the first member 20 and the second member (not shown) are relatively rotatable, and is provided such that the rotation torque changes depending on the rotation angle. ing.

  The first member 20 and a second member (not shown) are connected by a shaft portion 22. One end 22a of the shaft 22 is attached to the first member 20 so as to be rotatable. The other end portion 22b of the shaft portion 22 is a side attached to the second member, and here, each plate serves as a pressing portion for pressing a plurality of disc springs, which will be described later, to the first member 20 side. A flange portion 22b having a diameter larger than that of the spring is formed.

  A caulking member 40 for preventing the shaft portion 22 from coming off from the first member 20 is attached to one end portion 22 a of the shaft portion 22. The caulking member 40 is formed with a through hole 46 having the same shape as the cross-sectional shape of the shaft portion 22. One end 22a of the shaft portion 22 protruding through the first member 20 is inserted into the through hole 46 of the caulking member 40, and the shaft portion 22 and the caulking member 40 are fixed by caulking.

The first member 20 may have any shape depending on the structure of the device to be attached, but in the present embodiment, a planar planar portion 23 to which the shaft portion 22 is vertically attached and a planar portion 23. And a fixing portion 25 which is raised vertically. A fixing hole 27 is formed in the fixing portion 25.
Further, the flat portion 23 of the first member 20 is formed with a fixing hole 31 that is formed to penetrate one end portion 22a of the shaft portion 22 and to fix a fixing portion 29 of the first cam 28 described later. ing.

The shaft portion 22 is provided with a first cam 28 that is fixed to the first member 20 and does not rotate, and a second cam 32 that meshes with the first cam 28. Each of the first cam 28 and the second cam 32 is formed with through holes 28 a and 32 a for allowing the shaft portion 22 to pass through the center.
Further, as described above, the side of the first cam 28 facing the first member 20 (the upper side in the drawing) is a fixing portion 29 that is fitted into the fixing hole 31 of the first member 20. Since the fixing portion 29 and the fixing hole 31 are not circular but have the same shape having a straight portion, the fixing portion 29 inserted into the fixing hole 31 is fixed to the first member 20 without rotating. The

A plurality of disc springs are arranged on the second member side (lower side in the drawing) of the second cam 32. In this embodiment, one first disc spring 34 (low load disc spring) that is deformed with a low pressure is disposed at a position in contact with the second member side surface (lower side in the drawing) of the second cam 32, Four second disc springs 36 (high load disc springs) that are deformed by a high pressure are arranged on the second member side surface (lower side in the drawing) of the disc spring 34.
Each of the first disc spring 34 and the second disc spring 36 is formed with through holes 34 a and 36 a for allowing the shaft portion 22 to pass through the center.

Next, FIGS. 3 to 6 show side surfaces on which the first cam 28, the second cam 32, the first disc spring 34, and the second disc spring 36 are arranged along the shaft portion 22. In these drawings, the actual disc spring is thicker, but is shown thin in the drawings.
In the present embodiment, the first cam 28, the second cam 32, the first disc spring 34, and the second disc spring 36 all have the same diameter. Therefore, it is possible to configure the hinge device 30 that can reduce the rotation space without requiring a large space. In the present invention, the rotation torque can be changed by the rotation angle in this space.
However, the first cam 28, the second cam 32, the first disc spring 34, and the second disc spring 36 do not necessarily have the same diameter, but at least the diameters of the first cam 28 and the second cam 32 are It is necessary that the diameter is larger than the diameter of the first disc spring 34 and the second disc spring 36.

The structure of the first cam 28 and the second cam 32 will be described.
On the second cam 32 side (downward in the drawing) of the first cam 28, a recess 39 that is recessed toward the first member 20 (upward in the drawing) is formed. The peripheral wall surface forming the recess 39 is formed with a vertically formed vertical surface 45 and a tapered surface 41 that is inclined in a direction in which the recess 39 gradually expands toward the second cam 32 (downward in the drawing). ing.
On the first cam 28 side (upward in the drawing) of the second cam 32, a convex portion 42 that protrudes toward the first cam 28 so as to enter the concave portion 39 of the first cam 28 is formed. The protruding length of the convex portion 42 is such a length that the upper surface 42 a of the convex portion 42 contacts the lower surface 39 a of the concave portion 39 when the convex portion 42 enters the concave portion 39. Further, the height of the convex portion 42 needs to be such that the bottom surface of the first cam 28 and the top surface of the second cam 32 do not come into contact with each other.

Next, the disc spring will be described.
Of the disc springs arranged on the second member side (lower side of the drawing) of the second cam 32, the disc spring arranged at the closest position to the second cam 32 is a first disc spring that is deformed with a low pressure. 34.
In general, the disc spring is a thin disk-shaped plate material, and when viewed from the side, the periphery of the through hole that penetrates the shaft portion 22 is planar, but the periphery is formed to be inclined toward the center direction. . Due to this inclination, when a pressure is applied to the disc spring, a predetermined pressure can be applied to the contacting portion by the elastic force of the inclined portion.
The first disc spring 34 that is deformed at a low pressure is formed thinner than the second disc spring 36, so that the first disc spring 34 is deformed at a lower pressure than the second disc spring 36, and the low pressure When applied, pressure can be applied to the object.

On the second member side (lower side of the drawing) of the first disc spring 34, four second disc springs 36 that are deformed by a high pressure are arranged in an overlapping manner.
Since each second disc spring 36 is formed thicker than the first disc spring 34, it does not deform unless a pressure higher than that of the first disc spring 34 is applied.
In the present embodiment, four second disc springs 36 are arranged so as to overlap each other, but are arranged so that their inclination directions are staggered. That is, the four second disc springs 36 are sequentially arranged from the first disc spring 34 side so as to be concave upward, and are arranged so as to be concave downward. It comprises a second disc spring 36b, a second disc spring 36c arranged to be concave upward, and a second disc spring 36d arranged to be concave downward.

4 to 6 show the first member 20 rotated relative to the shaft portion 22.
In FIG. 4, the convex portion 42 of the second cam 32 is completely accommodated in the concave portion 39 of the first cam 28. In this state, when the first cam 28 is rotated in the right direction in the drawing, the upper surface 42a of the convex portion 42 of the second cam 32 is rotated within a range where the upper surface 42a is in contact with the lower surface 39a of the concave portion 39 (in the range a). In this state, the disc springs 34 and 36 are compressed in the arrangement direction between the flange portion 22b of the shaft portion 22 and the second cam 32, but only the first disc spring 34 is deformed to generate pressure. The four second disc springs 36 are provided so as not to be deformed and not to generate pressure. The rotational torque at this time is low torque, and its magnitude is constant.

Then, as shown in FIG. 5, when the first cam 28 rotates and the convex portion 42 of the second cam 32 contacts the tapered surface 41 in the concave portion 39 of the first cam 28, the convex portion 42 is Ride on the tapered surface 41. Then, the second cam 32 gradually moves along the inclination of the taper surface 41 while moving the disc springs 34 and 36 toward the flange portion 22b while compressing the disc springs 34 and 36 (arrow b). .
Then, the 1st disc spring 34 which deform | transforms with a low pressure deform | transforms so that an inclined part may become planar shape, and the pressure accompanying this deformation | transformation is produced. The rotational torque at this time is associated with the action of the first disc spring 34, and gradually increases according to the rotational angle, but the amount of change in the magnitude of the torque is small.
In this way, the torque is gradually increased when switching from low torque to high torque, so that the torque can be gradually increased without suddenly increasing. The feeling of strangeness can be eliminated.

Next, as shown in FIG. 6, when the first cam 28 further rotates, the convex portion 42 of the second cam 32 comes out of the concave portion of the first cam 28 and contacts the bottom surface 28 b of the first cam 28. Then, the second cam 32 further presses the disc springs 34 and 36, and the inclined portion of the first disc spring 34 is completely flat. After this state, even if the first disc spring 34 is further pressed, it is not further deformed and remains in a simple washer state.
When the first disc spring 34 is deformed into a flat shape and is not further deformed, the second cam 32 deforms each second disc spring 36.
Each of the second disc springs 36 is pressed by the second cam 32 and compressed and deformed in the arrangement direction, and generates a pressure associated with the deformation. The rotational torque at this time is accompanied by the action of the second disc spring 36, is high torque, and its magnitude is constant.

Next, FIGS. 7 to 8 show the relationship between the amount of spring deflection and the spring load when the first disc spring 34 and the second disc spring 36 are pressed. The rotational torque increases as the spring load increases.
As the first disc spring 34 is pressed, the relationship between the deflection amount and the spring load becomes a proportional relationship, and the spring load increases linearly as the deflection amount increases.
On the other hand, when the second disc spring 36 is pressed, the relationship between the amount of deflection and the spring load becomes a proportional relationship, but becomes a straight line having a larger inclination than the first disc spring 34.

FIG. 9 shows the relationship between the rotation angle and the spring load in this embodiment.
First, in the state of FIG. 4, the convex portion 42 of the second cam 32 rotates in a state of being fitted in the concave portion 39 of the first cam 28, and only the spring load of the first disc spring 34 is obtained. Acts and the spring load is constant.

When the convex portion 42 of the second cam 32 rotates on the tapered surface 41 of the first cam 28 as in the state of FIG. 5, the first disc spring 34 gradually collapses. The spring load increases linearly with the rotation angle.
When the convex portion 42 of the second cam 32 rotates in contact with the bottom surface 28a of the first cam 28 as in the state of FIG. 6, the first disc spring 34 becomes a simple washer, Only the spring load of the second disc spring 36 acts, and the spring load is constant.
Thus, in this embodiment, when the 1st member 20 and the 2nd member are rotated relatively, the operation load at the time of rotation is a fixed low load to a certain rotation position, and this When it is further rotated from the rotation position, the operation load at the time of rotation gradually increases, and then becomes a constant high operation load.

In the present embodiment, one first disc spring 34 and four second disc springs 36 are used, and the second disc springs 36 are arranged so that the inclination directions are staggered.
However, the hinge device of the present invention is not limited to such a configuration. That is, the required number of the first disc springs 34 and the second disc springs 36 can be changed as appropriate in accordance with the torque required during rotation. Further, the arrangement direction of the inclined portions of the second disc springs 36 may also be arranged so that the inclination directions are the same.
However, if the disc springs are arranged so that the inclination directions are the same, the spring load is quadrupled even with the same deflection amount than when the disc springs are arranged so that the inclination directions are staggered. Therefore, the arrangement of the disc springs in the tilt direction may be determined in accordance with the torque required during rotation.

Moreover, you may comprise so that a click feeling may be given when it becomes a predetermined rotation angle (not shown).
In order to give a feeling of clicking, a concave and convex portion for fitting the concave and convex portions is provided at a location where the first cam 28 and the second cam 32 contact each other, and the first cam 28 and the second cam 32 are relatively at a predetermined angle. When it becomes, what is necessary is just to comprise so that a convex part may fit in a recessed part.

  In addition, the hinge device of the present invention is not limited to use in a display device for a passenger car, and any device can be used as long as the torque changes according to the rotation angle. can do.

20 First member 22 Shaft portion 23 Flat portion 25 Fixing portion 27 Fixing hole 28 First cam 29 Fixing portion 30 Hinge device 31 Fixing hole 32 Second cam 34 First disc spring 36 Second disc spring 39 Recess 40 Caulking member 41 Tapered surface 42 Convex portion 45 Vertical surface 46 Through hole

Claims (3)

In the hinge device in which the first member and the second member are mounted so as to be relatively rotatable, and the rotation torque changes depending on the rotation angle.
A first member;
The other end portion is fixed to the second member, and the one end portion is rotatably attached to the first member;
A first cam fixed to the first member;
A second cam having the same diameter as that of the first cam, which is formed so as to mesh with the first cam, and is fixed to the shaft portion and rotatable together with the shaft portion;
A plurality of disc springs having the same diameter as the first cam and the second cam, arranged to penetrate the shaft portion so as to press the second cam against the first cam;
Each of the disc springs includes a first disc spring that is deformed with a low pressure and a second disc spring that is deformed with a high pressure. The first cam and the second cam have a recess formed in one of them, and a protrusion that can enter the recess is formed in the other.
2. The hinge device according to claim 1, wherein a side of the concave portion from which the convex portion is detached from the concave portion is formed in a tapered shape so that the convex portion is gradually separated.   The hinge device according to claim 1 or 2, wherein the first disc spring is provided in one piece and the second disc spring is provided in two pieces.