JP4594135B2 - Friction torque hinge - Google Patents

Description

  The present invention relates to a friction torque hinge that is attached to an opening / closing center portion of a rotary opening / closing body and is formed so that a rotational resistance is generated between one side member and the other side member that are rotatable between each other.

  For example, hinges used for various revolving doors and mechanical device covers are called hinges, so that the doors do not open too lightly, so that the doors have a high-class feel and the covers are held at a certain degree of opening. In addition, a friction torque hinge is known in which a rotational resistance is added to the rotary opening / closing body.

As the structure of the rotational resistance applying portion, the conical shaft coupled to the cover of the notebook computer that is one side member of the opening / closing body is fitted into the conical boss coupled to the main body of the personal computer that is the other side member. The boss side is biased in the direction of the conical axis via three disc springs arranged side by side, and the biasing force is changed to a surface pressure by a perpendicular force perpendicular to the conical contact surface. The frictional force that is generated gives rotation resistance when opening and closing the PC cover. (See Patent Document 1).
Japanese Patent Laid-Open No. 2004-003594 (FIG. 3 and related explanation of the specification)

  However, in such a conical shaft type hinge, since the conical surface is a curved surface and an inclined surface, it is difficult to obtain a full contact state between the shaft and the boss in terms of processing accuracy and the like. A stable rotation resistance cannot be obtained.

  Also, since the torsional rigidity of the shaft is inversely proportional to the fourth power of the shaft diameter, in the direction in which the shaft diameter of the conical shaft becomes thinner, the vertical force due to the surface pressure on the cross section having a constant width in the axial direction decreases with the first power of the shaft diameter. However, since the torsional rigidity greatly decreases, the vertical force eventually decreases, and as a result, the surface pressure of the thick portion of the conical shaft becomes excessive, so that a large spring force cannot be applied. Further, for example, even if the cone apex angle is set to a sufficiently small angle, for example, 10 °, the vertical force is only about 5.5 times the spring force of one disc spring. Therefore, there may be a case where it is not possible to obtain a sufficiently large rotational resistance as required.

  Accordingly, an object of the present invention is to provide a friction hinge that can solve such a problem in the prior art and can stably obtain a large rotational resistance as required.

In order to solve the above-described problems, the present invention provides a rotational resistance between one side member (1) and the other side member (2) that are attached to the opening / closing center of the rotary opening / closing body and are rotatable between each other. In the friction torque hinge formed as described above, the shaft (3) of the outer diameter d provided integrally with the one side member (1) so as to be the center of the opening / closing center portion , A flat portion (3a) with a part cut off, and a cylindrical shape having an inner diameter D provided integrally with the other side member (2) at a distance (12) concentrically with the shaft (3). a portion (4), a portion without becoming a complete cylinder to that a gap (4a), placed in the gap (12) to rotate integrally with the shaft (3), said shaft shaft side friction surface consisting of axially oriented plane is the direction of (3) (5b, 5c) to the inner diameter A plurality of shaft side friction member (5), said cylindrical portion (4) and placed in the gap (12) to rotate integrally the shaft side friction surface with the flat surface portion and (5a) projecting ( A plurality of cylinder-side friction members (6) having a cylindrical-side friction surface (6b) having a flat surface formed so as to come into contact with 5b, 5c) and a protrusion (6a) formed on the outer diameter side; The shaft-side friction member (5) and the cylinder-side friction member (6) are configured so that the shaft-side friction surfaces (5b, 5c) and the cylinder-side friction surface (6b) can be pressed against each other. A disc spring (7) provided at least at one end side in the axial direction of the member portion and a plurality of positions in the middle; and a compression member (8, 9) for compressing the disc spring (7) in the axial direction; the a, wherein the axial-side friction member (5) and said cylindrical side friction member (6), except for the projecting portion (6a) Wherein is formed to be slightly smaller with inner and outer diameters slightly larger than the d than D, flat portion of the shaft side friction member flat portion and (3a) of the shaft (3) (5) and (5a) Are in plane contact, and the protrusion (6a) enters the gap (4a) .

According to the present invention, the shaft and the cylindrical shape are included in the interval between the shaft provided integrally with the one side member and the cylindrical portion provided concentrically with the shaft integrally with the other side member. A plurality of shaft-side friction members and cylinder-side friction members are inserted so as to rotate integrally with each part, and the shaft-side friction surface and the cylinder-side friction surface, which are flat in the axial direction, are pressed against each other by a disc spring. Since the disc springs are provided at least at one end side in the axial direction and at a plurality of positions in the middle and are compressible in the axial direction by the compression member, one side and the other side of the friction hinge are For example, when it is attached to the rotation center of the door as a rotary opening / closing body and the disc spring is tightened by the compression member, the door is rotated to rotate between the one side member and the other side member. Give the door the desired rotational resistance It can be.

  That is, when the disc spring is tightened by the compression member, the compression force is transmitted to a plurality of contact surfaces in contact with the friction surfaces on the shaft side and the cylinder side, and the friction caused by the surface pressure corresponding to the compression force is applied to this surface when the door is opened and closed. A force is generated, and a corresponding friction torque acts on the door as a rotational resistance. Since this rotational resistance is determined by the spring force of the disc spring, the shape, size and number of friction surfaces, and the friction coefficient, these rotational resistances are determined so as to generate the intended rotational resistance.

  In this case, since both the shaft-side friction surface and the cylinder-side friction surface are flat, a full contact state can be easily obtained at these contact surfaces, and a uniform contact pressure is generated on the entire surface. As a result, the disc spring force can be increased so as to increase the surface pressure as much as possible within the allowable limit of the surface pressure depending on the material of the member, and a stable and uniform rotational resistance can be obtained.

  In addition, the hinge requires that the cylindrical portion be sufficiently small in size, and one friction surface cannot be enlarged, but the axial length can be freely determined to some extent, so the number of friction surfaces The desired rotational resistance can be easily obtained by increasing the number as necessary.

  In addition, since the disc spring generates a large spring force even if its size is small, it is an optimal member for generating a rotational resistance in terms of the spring force. However, since the amount of deformation is small relative to the spring force, it is difficult to adjust the spring force when compressing with the compression member. On the other hand, in the present invention, since the disc spring is provided at least on one end side in the axial direction of the friction member portion, and a plurality of disc springs are provided in the middle, compression force can be favorably applied to all the friction surfaces. At the same time, the amount of compression of the disc spring is increased by a factor of several with respect to the same compression force, so the amount of compression increases and the ease of adjusting the compression force is ensured.

  FIG. 1 shows an example of the overall configuration of a friction torque hinge to which the present invention is applied, and FIG. 2 shows an example of a portion of a shaft side ring and a cylinder side ring and a structure portion of a disc spring.

  A friction torque hinge (hereinafter, simply referred to as “friction hinge” or “hingle”) is attached to the opening / closing center of the rotary opening / closing body and is configured to rotate between the blade 1 and the blade 1. It is a hinge formed so that rotational resistance is generated between the blade 2 that is the other side member, the shaft 3, the outer cylinder 4 that is the cylindrical portion, the shaft side ring 5 that is the shaft side friction member, the cylinder side It is comprised by the cylinder side ring 6 which is a friction member, the disk spring 7, the adjustment nut 8 as a compression member, the fixed nut 9, etc.

  The blades 1 and 2 are provided with appropriate numbers of mounting holes 1a and 2a, so that each of the blades 1 and 2 serves as a rotation opening / closing body, for example, a rotation center line C of a rotary door of a room. Attached to the center and door frame. A portion of the upper half of the blade 2 on the side of the center line C is formed in a cylindrical shape and forms the outer cylinder 4. A cylinder 10 is formed in the lower half of the blade 1.

  The shaft 3 is provided integrally with the blade 1. In this example, an intermediate cylinder 11 having a flange 11 a is press-fitted into the cylinder 10 of the blade 1 so as to be integrated with the blade 1, and is inserted into the intermediate cylinder 11. The lower end portion of the blade 1 is integrated with the blade 1 by being welded thereto. The center of the shaft 3 is the center line C. As a result, when the door is rotated and the blade 1 is rotated, the shaft 3 is also rotated at the same time. As shown in FIG. 2 (a), the shaft 3 is a cylindrical body having a shape of a flat surface portion 3a in which a part of the circular cross section is missing. A screw 3b is cut at the upper end.

  The outer cylinder 4 is provided concentrically with the same center line C as the shaft 3 integrally with the blades 2 with an interval 12 shown in FIG. That is, the gap 12 is provided between the inner diameter D of the outer cylinder 4 and mainly the outer diameter d of the shaft 3. FIG. 2 (b) is a diagram showing only the shaft 3 and the outer cylinder 4 in combination. The outer cylinder 4 is formed integrally with the blade 2 as described above. Further, a gap 4a is formed in a part of the cylinder, not a complete cylinder.

  The shaft-side ring 5 is formed in an annular shape and is composed of 16 pieces as a plurality in this example, and is inserted in the interval 12 so as to rotate integrally with the shaft 3. That is, as shown in FIG. 2 (c), a hole having an inner / outer diameter slightly smaller than the inner diameter D of the cylinder 4 and slightly larger than the outer diameter d of the shaft 3 and a flat portion 5a protruding toward the inner diameter side is formed. As shown in FIG. 2 (d), the flat portion 5a and the flat portion 3a come into flat contact with each other when the flat portion 5a is brought into contact with the shaft 3 as shown in FIG. Is transmitted and is integrally rotated. Although not shown in the figure, the portion for transmitting torque may be formed into other appropriate structures such as an uneven portion or using a key and a key groove.

  As shown in FIG. 2E, the shaft-side ring 5 includes a shaft-side friction surface 5b or 5c composed of a plane facing the Z direction that is the axial direction. The shaft-side friction surface 5b or 5c is also a substantially double circle having the same inner and outer diameters as those of the shaft-side ring 5 and D and d. The shaft-side ring 5 has surfaces on both sides in the Z direction. In this example, one side is a shaft-side friction surface that comes into contact with a cylinder-side friction surface 6b described later. However, as an actual product, the other surface, which will be the support surface of the disc spring 7 described later, is usually processed in the same manner, so that both surfaces can be friction surfaces.

  The cylinder-side ring 6 is formed in an annular shape, and is configured as a plurality of half of the shaft-side ring 6 in this example, and is inserted into the interval 12 so as to rotate integrally with the outer cylinder 4. That is, as shown in FIGS. 2 (f) to 2 (h), the same inner and outer diameters as the shaft side ring 5 are formed, the protruding portion 6 a is formed on the outer diameter side, and the inner diameter side is fitted into the shaft 3. It is disc-shaped, and when the projection 6a is fitted into the shaft 3, the protrusion 6a enters the gap 4a of the outer cylinder 4 and comes into contact with both end surfaces forming the gap 6a. Torque is transmitted so as to rotate integrally. It should be noted that the portion for transmitting the torque may have a normal appropriate structure such as an uneven portion or a key as described above.

  The cylinder side ring 6 is provided with a cylindrical friction surface 6b that is in contact with the shaft side friction surface 5b. Similar to the shaft side friction surface 5b, this surface also has a substantially double circular shape having substantially inner and outer diameters D and d. Although the cylindrical ring 6 also has surfaces on both sides in the Z direction, in this example, it is half of the shaft side ring 5, so that the cylindrical side friction surface 6b whose both side surfaces are in contact with the shaft side friction surface 5b. It has become.

  In the above description, the number of the shaft side rings 5 is 16 and the number of the cylinder side rings 6 is 8. However, the number of both rings may be the opposite number. In that case, the disc spring put between the shaft side rings is put between the tube side rings 6 as described later.

  The disc spring 7 has the shape shown in FIG. 2 (i), and the shaft-side ring 5 and the cylinder-side ring 6 are configured so as to be able to press-contact between the shaft-side friction surface 5b and the cylinder-side friction surface 6b. At least one end side in the Z direction of the configured friction member portion 13 in this example as both ends and in the middle, in this example, in a portion between the 16 shaft side rings 5 in this example, a total of a plurality of locations at positions alternately with the cylinder side ring 6 Nine locations are provided.

  According to such an installation state of the disc spring 7, the disc spring 7 is arranged in a well-balanced manner on the entire friction member portion 13, and the upper and lower ends 7 a and 7 b thereof are the shaft-side friction surface 5 b or the shaft-side ring 5. Since it is stably supported by, for example, the plane of 5c on the side of 5c that is not the friction surface, the same spring force can be stably generated in a balanced manner throughout the friction member portion 13. Note that the number and setting positions of the disc springs 7 can be changed as appropriate according to the necessary spring force of the disc springs, which differs depending on the type of rotary opening / closing body to which the friction torque hinge is applied.

  The adjusting nut 8 and the fixing nut 9 make the disc spring 7 compressible in the Z-axis direction. That is, in this example, the disc spring 7 is compressed by the adjusting nut 8 to determine the amount of compression, and the position of the adjusting nut 8 is fixed by the fixing nut 9 so that the compression position cannot be easily changed. In addition, as a compression member, only an adjustment nut may be sufficient according to the kind of rotary opening-closing body to which a friction torque hinge is applied, an attachment location, etc.

Such friction hinges are used for building doors, for example. At that time, the outer diameter D ₁ of the outer cylinder 4 is limited to a sufficiently small dimension from the viewpoint of the appearance of the door, and as a result, the inner diameter D and the outer diameter d of the shaft 3 are also made smaller. -D) The dimensions of the shaft-side and cylinder-side rings 5 and 6 and the corresponding disc springs 7 that are put in the interval 12 part are often made small. The disc spring 7 generates a remarkably large spring force with a small area and a bending amount as compared with other springs, but still has a small size, so the spring force F cannot be extremely increased.

In such a friction hinge, for example, the outer diameter D ₁ = 16 mm, the inner diameter D = 11 mm, the outer diameter d of the shaft 3 is 5 mm, the maximum spring force Fmax is 370 N, and the friction surface between the rings 5 and 6 is as shown in FIG. 16 faces. When the disc spring 7 is tightened with this friction hinge, the tightening force is transmitted as a compression force to the 16 contact surfaces serving as friction surfaces, and a frictional force is generated corresponding to this compression force when the door is opened and closed. The corresponding friction torque acts on the door as rotational resistance. This rotational resistance is determined by the spring force F of the disc spring, the shape and size of the friction surface, that is, the values and numbers of D and d, and the friction coefficient.

Therefore, if the friction coefficient of the friction surface is set to 0.2, and a total of eight disc springs 7 are tightened to a total of about 2.4 mm and the operating spring force F _{1 is set} to 300 N, detailed calculation is omitted, The friction torque T generated by the number is about 4100 N-mm. Therefore, if the handle portion of the door is at a position of 800 mm from the hinge, a pushing / pulling force of about 5 N can be applied to the handle portion when the door is opened and closed. That is, a sufficiently small-sized friction hinge can make the door opening / closing structure somewhat resistant but with some resistance. In this case, the surface pressure of the friction surface is about 25 N / mm ^2, which is within the allowable surface pressure of a true casting or steel plate as a material of the ring.

  According to such a friction hinge, since the friction surface is flat, the entire contact state can be easily obtained by the flatness achieved by normal surface processing, so that uniform surface pressure is generated on the entire surface. Can be made. As a result, it is possible to obtain a large frictional force by bringing the surface pressure of the friction surface close to the allowable surface pressure as described above, and it is possible to obtain a stable, uniform and large rotational resistance.

Furthermore, even if sufficiently small dimensions an outer diameter D ₁ of the outer cylinder 4 as in this embodiment, it is possible to provide a large number of friction surface as needed in the Z-direction, to easily obtain a rotation resistance for the purpose be able to.

FIG. 3 shows another example of a friction hinge to which the present invention is applied.
In the friction hinge shown in FIG. 1, a total of eight disc springs 7 are provided between all of the two shaft side rings 5 between the cylinder side rings 6. As shown in the figure, four cylinder-side rings 6 are added between the other four locations, as shown in the figure. As a result, the number of the springs 7 is reduced to four, but the friction surface is increased by four by the cylinder side ring 5 increased by four to a total of 24 surfaces, so that the rotational resistance T is set to about 6200 N-mm. The pushing / pulling force of the handle when the door is opened / closed can be about 7.8N.

  If the friction hinge as shown in FIG. 1 is used, since there are eight disc springs 7, the tightening amount is set to a large value of about 2.4 mm with respect to the same tightening force F, thereby facilitating the tightening operation and accuracy. The tightening force F can be applied well, and the compression force of the friction surface can be made uniform by applying the compression force of the countersink 7 to both sides of all the 16 friction surfaces via the tube side ring 6. On the other hand, according to the friction hinge shown in FIG. 3, although the spring constant of the entire spring system of the friction member portion 13 becomes high and the tightening adjustment of the disc spring 7 becomes somewhat difficult, the rotation resistance is reduced by 50 with the same size friction hinge. % Can be increased.

  The friction torque hinge of the present invention is particularly advantageously used for a part such as a cover of office equipment that is required to maintain a middle open state, for example, when a door has a high-class feeling in a superior room.

It is a front view which shows the center in an example of the whole structure of the friction torque hinge to which this invention is applied by a longitudinal cross-section. (A) thru | or (i) show an example of the partial structure of the said hinge, (a) is a cross-sectional view of a shaft, (b) is a cross-sectional view of a shaft and an outer cylinder part, (c) is a shaft side ring. (D) is a cross-sectional view of the shaft-side ring portion, (e) is a vertical cross-sectional view of the shaft-side ring, (f) is a plan view of the tube-side ring, and (g) is a vertical cross-section of the tube-side ring. (H) is a cross-sectional view of the cylindrical ring portion, and (i) is a vertical cross-sectional view of the disc spring. It is a front view which shows the center in the longitudinal cross-section in the other example of the whole structure of the friction torque hinge to which this invention is applied.

Explanation of symbols

1 blade (one side member)
2 blades (other side member)
3 axis
4 outer cylinder (cylindrical part)
5 Shaft side ring (shaft side friction member)
5b, 5c Shaft side friction surface 6 Cylinder side ring (cylindrical side friction member)
6b Cylindrical friction surface 7 Belleville spring 8 Adjustment nut (compression member)
9 Fixing nut (compression member)
12 Interval 13 Friction member part C Center line (opening / closing center)
Z-axis direction (axis direction)

Claims (1)

In a friction torque hinge that is attached to the opening / closing center part of the rotary opening / closing body and is formed so that rotational resistance is generated between the one side member (1) and the other side member (2) that can rotate between each other,
It is a shaft (3) having an outer diameter d provided integrally with the one side member (1) so as to be the center of the opening / closing center portion, and is a flat portion (3a) in which a part of the circular cross section is missing. And what
Wherein a second side member (2) and a cylindrical portion having an inner diameter D spaced (12) coaxially with said axis integral (3) (4), a portion without becoming a complete cylinder Is a gap (4a) ,
Placed in the gap (12) so as to rotate integrally the shaft (3), said shaft (3) shaft side friction surface consisting of axially oriented plane is the direction of the (5b, 5c) and the inner diameter side A plurality of axial friction members (5) provided with a protruding flat surface portion (5a) ;
Said cylindrical portion (4) integral said placed in intervals (12) to rotate the shaft side friction surface (5b, 5c) made of formed flat so as to be in contact with the cylindrical side friction surface and (6b) A plurality of cylindrical friction members (6) having protrusions (6a) formed on the outer diameter side;
Friction member composed of the shaft side friction member (5) and the cylinder side friction member (6) so that the shaft side friction surface (5b, 5c) and the cylinder side friction surface (6b) can be pressed against each other. A disc spring (7) provided at least at one end side in the axial direction of the portion and at a plurality of positions in the middle;
Has a compression member (8,9) to allow compression of the Belleville spring (7) in the axial direction,
The shaft-side friction member (5) and the cylinder-side friction member (6) are formed to have inner and outer diameters slightly smaller than the D and slightly larger than the d , except for the protrusion (6a). And
The flat surface portion (3a) of the shaft (3) and the flat surface portion (5a) of the shaft-side friction member (5) are in plane contact, and the protruding portion (6a) enters the gap (4a). Characteristic friction torque hinge.

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