JP2020002967A - Spiral spring device - Google Patents

Abstract

To provide a spiral spring device capable of improving torque characteristics of a spiral spring, and extending a use range.SOLUTION: A spiral spring device comprises a spiral spring 2 having a non-contact structure in which the interval between spirally wound plate materials gradually increases from an inner end to an outer end, and a case 3 accommodating the spiral spring 2 such that the inner end 6 of the spiral spring 2 is on the rotating side and the outer end 7 is on the stationary side. The case 3 is provided with a forced displacement member 4 that abuts on the outside of the plate 5 near a 3/4 turn portion from the outer end 7 of the spiral spring 2 to forcibly displace the plate 5 radially inward.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a spiral spring device used for devices such as a reclining device of an automobile, a window regulator, and a pointer of a measurement meter.

  FIG. 11 shows a spiral spring 100 used in the above-described device. The spiral spring 100 is formed in a non-contact structure in which the interval (pitch) between the plate members 130 gradually increases from the inner end 110 to the outer end 120 and is housed in the case 200 of the device. The inner end 110 is on the rotating side by being hooked on a rotating shaft 210 on the device side inserted in the case 200, and the outer end 120 is being hooked on a fixed shaft 220 on the device side inserted in the case 200. As a result, the device is operated and the device is operated to be tightened from the inner end 110 side.

  When the spiral spring 100 is tightened, as shown in FIG. 12, the entire spring is shifted in a translational direction in the direction of approximately ／ of the winding from the outer end 120, and is displaced. For this reason, in the 巻 き turn portion on the opposite side, the plate material 130 is deviated so that the pitch of the plate members 130 becomes denser than in other portions, and local plate-to-plate contact occurs. This causes problems such as generation of abnormal noise and fluctuation of torque characteristics.

  On the other hand, Patent Literature 1 discloses a structure for preventing a spiral spring from contacting between plates. In this structure, a regulating member for regulating the displacement caused by rotating the inner end is provided at the 1/4 turn or 3/4 turn from the outer end of the spiral spring. Specifically, a restricting member is interposed between the plate members at the 1/4 turn from the outer end to prevent the inward displacement of the 1/4 turn, or at the 3/4 turn from the outer end. A restricting member is arranged outside the plate material to prevent the 3/4 turn portion from being displaced outward.

Japanese Utility Model Publication No. 49-145060

  However, in the structure of Patent Document 1, there is still a limit in improving the torque characteristics. FIG. 13 is a characteristic diagram obtained by measuring a torque characteristic when a regulating member is provided at a 3/4 turn from the outer end described in FIG. 2 of Patent Document 1. In FIG. 13, a plate material having a plate thickness of 0.81 mm, a plate width of 9 mm, and a total length of 600 mm is wound in a spiral manner in a non-contact state at an equal pitch as described in FIG. 2 of Patent Document 1. Curve A shows a torque change at the time of tightening, and curve B shows a torque change at the time of rewinding.

As shown in FIG. 13, in the structure of Patent Document 1, the gap between the torque at the end of the tightening and the torque at the beginning of rewinding is greatly increased by the tightening in the range of the number of rotations of 1.5, and thereafter, gradually. Since it approaches the winding side, the restoring force of the spiral spring cannot be fully utilized. In the structure of Patent Document 1, since the difference in torque change between the time of tightening and the time of rewinding is large, there is a limit to the improvement of the torque characteristics, and the range of use of the tightening and rewinding cannot be expanded. Have a point.
The present invention has been made in view of such problems, and has as its object to provide a spiral spring device capable of improving the torque characteristics of the spiral spring and expanding the range of use. To be

  The spiral spring device according to the present invention includes a spiral spring having a non-contact structure in which the interval between the spirally wound plate members gradually increases from the inner end to the outer end; A case for accommodating the spiral spring such that the end is on the fixed side, wherein the spiral spring is forcibly displaced radially inward by abutting against the outside of the plate near the 3/4 turn from the outer end of the spiral spring. The case is characterized in that the case is provided with a forced deflection member.

  Further, the spiral spring device of the present invention includes a spiral spring having a non-contact structure in which the interval between the spirally wound plate members gradually increases from the inner end to the outer end; A case for accommodating the spiral spring such that the outer end is on the fixed side, and forcing the plate radially outward by contacting the inside of the plate near the quarter turn from the outer end of the spiral spring. It is characterized in that the case is provided with a forced deflection member for deflection.

  The forcibly displaced member is forcibly displaced such that adjacent plate members are kept in a non-contact state with each other when the spiral spring is tightened by the rotation of the inner end.

  According to the present invention, the forcibly displacing member is brought into contact with the vicinity of the 3/4 turn portion from the outside to forcibly displace the plate material inward in the radial direction, or the forcibly displaced member is disposed near the 1/4 turn portion. Since the plate member is forcedly displaced radially outward by contacting from the inside, the torque characteristics of the spiral spring can be improved, and the range of use can be expanded.

It is a front view showing the spiral spring device of a 1st embodiment of the present invention. It is a front view showing an operation of a forced displacement member of a 1st embodiment. FIG. 4 is a characteristic diagram illustrating torque characteristics of the first embodiment. It is a front view showing the spiral spring device of a 2nd embodiment of the present invention. It is a front view showing an operation of a forced displacement member of a 2nd embodiment. FIG. 9 is a characteristic diagram illustrating a torque characteristic of the second embodiment. It is a front view showing a spiral spring device of a third embodiment of the present invention. It is a front view showing an operation of a forced displacement member of a 3rd embodiment. It is a front view showing the spiral spring device of a 4th embodiment of the present invention. It is a front view showing operation of a forced displacement member of a 4th embodiment. It is a front view which shows the conventional spiral spring of a non-contact structure. It is a front view showing operation of the conventional spiral spring. FIG. 9 is a characteristic diagram showing torque characteristics of a spiral spring described in Patent Document 1.

  Hereinafter, the present invention will be described specifically with reference to the illustrated embodiments. In each embodiment, the same members are denoted by the same reference numerals and correspond to each other.

[First Embodiment]
1 to 3 show a spiral spring device 1 according to a first embodiment of the present invention. As shown in FIGS. 1 and 2, the spiral spring device 1 includes a spiral spring 2, a case 3, and a forced deflection member 4.

  The spiral spring 2 is formed by spirally winding the plate material 5. The spiral spring 2 of the present invention is spirally wound so that the interval between the plate members 5 gradually increases from the inner end 6 to the outer end 7, and the adjacent plate members 5 inside and outside the spiral are in a non-contact state. Has become. Such a spiral winding can be performed, for example, along a logarithmic spiral.

  The case 3 is attached to a device such as a reclining device of an automobile, a window regulator, and a measurement meter. The case 3 is formed in an annular shape, and a rotation shaft (hinge shaft) 8 from the device is inserted into a central portion thereof, while a locking pin 9 from the device is inserted into an outer peripheral portion of the case 2. Have been. In the illustrated example, the rotating shaft 8 and the retaining pin 9 are located on the same line in the radial direction.

  The spiral spring 2 has a state in which the inner end 6 is hung on the rotating shaft 8 so that the inner end 6 is on the rotating side, and the outer end 7 is hung on the hooking pin 9 so that the outer end 7 is on the fixed side. And is housed inside the case 3. When the rotary shaft 8 rotates in one direction (clockwise), the spiral spring 2 is tightened. On the other hand, when the spiral spring 2 is rewound, the rotary shaft 8 rotates in the opposite direction (counterclockwise).

The forced deflection member 4 is provided in the case 3 and acts to abut the plate 5 inside the case 3 to forcefully shift the plate 5. In this embodiment, the forced deflection member 4 is formed in a shaft shape. The shaft-shaped forced displacement member 4 is provided on the case 3 so as to be located at a ３ turn from the outer end 7 of the spiral spring 2. The forced displacement member 4 abuts against the plate material 5 from the outside at the 3/4 turn, and forcibly displaces the plate material 5 inward in the radial direction.
Such forced displacement by the forced displacement member 4 causes a predetermined number of rotations of the inner end 6 (for example, a rotation speed of 1.5) even when the spiral spring 2 is tightened by the rotation of the inner end 6 (rotary shaft 8). In ()), the amount of forced displacement is adjusted so that the adjacent plate members 5 maintain a non-contact state with each other.

  FIG. 2 shows the operation of the forced deflection member 4. The dotted line indicates the state of the spiral spring 2 a when the forced deflection member 4 is not provided, and the solid line indicates the state of the spiral spring 2 when the forced deflection member 4 is provided. . When the forced displacement member 4 abuts on the 3/4 turn of the plate member 5 from the outside, the entire plate member 5 is displaced radially inward from the dotted line state to become the spiral spring 2 in the solid line state. As a result, the entire spiral spring 2 is displaced in the direction of the quarter turn.

When the rotating shaft 8 rotates clockwise and tightens the spiral spring 2 in the structure provided with such a forced displacement member 4, the spiral spring 2 is forcibly displaced from the beginning by the forced displacement member 4. No deviation in the direction of the 3/4 turn. For this reason, it is possible to suppress the pitch of the plate material 5 at the opposite 1/4 turn portion from becoming dense, and to prevent contact between the plate materials 5. Thereby, it is possible to prevent generation of abnormal noise and fluctuation of torque characteristics due to contact between plates.
Here, since the spiral spring 2 is wound so that the interval between the plate members 5 increases from the inner end 6 to the outer end 7, the contact between the plates within a predetermined rotation speed of the inner end 6 is further ensured. Can be prevented.

FIG. 3 shows torque characteristics of the spiral spring device 1 shown in FIG. 3, a plate member 5 having a plate thickness of 0.81 mm, a plate width of 9 mm and a total length of 600 mm is used as in FIG. Curve C is a characteristic plotting the torque changed by the number of rotations of the inner end 6 due to the tightening, and curve D is a characteristic plotting the torque changed by the rewinding.
As shown in FIG. 3, within the range of the rotation speed 1.5 of the inner end 6, the interval between the torque at the end of the tightening and the initial torque of the rewinding does not increase, and the curve C of the tightening does not change. The rewinding curve D is close. Therefore, since the difference in torque change between when tightening and rewinding is small, torque characteristics can be greatly improved, and the number of rotations of the rotating shaft 8 can be increased. The range can be expanded.

  In FIG. 1, the forcible displacement member 4 is in contact with the 3/4 turn, but any member may be used as long as it contacts the vicinity of the 3/4 turn including the 3/4 turn.

[Second embodiment]
4 to 6 show a spiral spring device 1A according to a second embodiment of the present invention.
Also in this embodiment, in the spiral spring 2, the plate material 5 is spirally wound, and the interval between the plate materials 5 gradually increases from the inside to the outside, so that they are not in contact with each other. The rotating shaft 8 from the device is inserted into the case 3, and the locking pin 9 from the device is inserted into the case 3. The spiral spring 2 is housed in the case 2 with the inner end 6 hooked to the rotating shaft 8 and the outer end 7 hooked to the hooking pin 9. The case 3 is provided with a forced deflection member 4.

As shown in FIGS. 4 and 5, the forced displacement member 4 of this embodiment is formed in a semicircular fin shape and provided in the case 3. The outer peripheral surface 12 of the forced displacement member 4 contacts the inner surface of the case 3, and the inner peripheral surface 11 faces the plate member 5 of the spiral spring 2. The inner peripheral surface 11 of the forcibly displaced member 4 is in contact with the outside of the plate 5 in a region including the 3/4 turn of the spiral spring 2, that is, in the vicinity of the 3/4 turn. 5 is forcibly displaced radially inward.
In this embodiment, since the forced deflection member 4 is formed in a semicircular fin shape, the contact length of the spiral spring 2 with the plate member 5 can be increased. For this reason, the forced displacement can be stably performed.

FIG. 5 shows the operation of the forced deflection member 4. As compared with the spiral spring 2a before the forced deflection shown by the dotted line in FIG. 5, the forced deflection member 4 abuts on the region including the 3/4 turn portion of the plate material 5 from the outside, so that the entire plate material 5 has a diameter. The spiral spring 2 is deflected inward in the direction, and becomes a spiral spring 2 in a solid line state. As a result, the entire spiral spring 2 is displaced in the direction of the quarter turn.
In this case, the forced deflection by the forced deflection member 4 is performed such that the adjacent plate members 5 are kept in non-contact with each other even when the spiral spring 2 is tightened by the rotation of the inner end 6 at a predetermined rotation speed. The forced displacement is adjusted.

When the rotating shaft 8 rotates clockwise and tightens the spiral spring 2 in a state in which the region including the 3/4 turn portion is forcibly displaced by the forcibly biasing member 4, the spiral spring 2 is forcedly biased. Since the displacement member 4 is forcibly displaced from the beginning, it does not shift in the direction of the 3/4 turn, and suppresses the dense pitch of the plate material 5 at the opposite 1/4 turn portion. Therefore, contact between the plates 5 can be prevented. Thereby, it is possible to prevent generation of abnormal noise and fluctuation of torque characteristics due to contact between plates.
Further, since the spiral spring 2 is wound so that the interval between the plate members 5 increases from the inner end 6 to the outer end 7, the contact between the plates within a predetermined rotation speed range of the inner end 6 is further ensured. Can be prevented.

FIG. 6 shows the torque characteristics of the spiral spring device 1A of this embodiment. Also in this embodiment, a plate member 5 having a plate thickness of 0.81 mm, a plate width of 9 mm, and a total length of 600 mm is used. Curve E is a characteristic plotting torque changed by the number of rotations of the inner end 8 due to winding, and curve F is a characteristic plotting torque changed by rewinding.
As shown in FIG. 6, in the range of the number of rotations 1.5 of the inner end 6, the torque at the end of the tightening and the initial torque of the rewinding are close to each other, so that the space between them is not opened, and And the rewinding curve F are close to each other. Therefore, since the difference in torque change between when tightening and rewinding is small, torque characteristics can be greatly improved, and the number of rotations of the rotating shaft 8 can be increased. The range can be expanded.

[Third embodiment]
7 and 8 show a spiral spring device 1B according to a third embodiment of the present invention.
As shown in FIG. 7, also in this embodiment, the spiral spring 2 is configured such that the plate 5 is spirally wound and the interval between the plate 5 gradually increases from the inside to the outside, so that the spiral spring 2 is not in contact with each other. It has become. The rotating shaft 8 from the device is inserted into the case 3, and the locking pin 9 from the device is inserted into the case 3. The spiral spring 2 is housed in the case 2 with the inner end 6 hooked to the rotating shaft 8 and the outer end 7 hooked to the hooking pin 9. The case 3 is provided with a forced deflection member 4.

The forced displacement member 4 of this embodiment is formed in a pin shape with a small diameter, and is provided on the case 3 so as to be located at a quarter turn from the outer end 7 of the spiral spring 2. The pin-shaped forced deflection member 4 abuts against the plate material 5 from the inside at the 1/4 turn portion to forcefully shift the plate material 5 radially outward.
The forced displacement by the forced displacement member 4 is such that even when the spiral spring 2 is tightened by the rotation of the inner end 6, the adjacent plate members 5 are not in contact with each other for a predetermined number of rotations of the inner end 6. The forced displacement is adjusted to keep it.

  FIG. 8 shows the operation of the forced deflection member 4. The dotted line indicates the state of the spiral spring 2 a when the forced deflection member 4 is not provided, and the solid line indicates the state of the spiral spring 2 when the forced deflection member 4 is provided. . When the forcibly displaced member 4 abuts on the quarter turn of the plate member 5 from the inside, the entire plate member 5 is displaced radially outward from the dotted line state to become the spiral spring 2 in the solid line state. As a result, the entire spiral spring 2 is displaced in the direction of the quarter turn.

  When the rotating shaft 8 rotates clockwise and tightens the spiral spring 2 in such a structure provided with the forced deflection member 4, the quarter turn of the spiral spring 2 is forcedly shifted outward from the beginning. Therefore, it does not shift in the direction of the 3/4 turn, and in the 1/4 turn portion, the pitch of the plate 5 can be suppressed from becoming dense, and the contact between the plates 5 can be prevented. . Thereby, it is possible to prevent generation of abnormal noise and fluctuation of torque characteristics due to contact between plates.

Also in this embodiment, since the spiral spring 2 is wound so that the interval between the plate members 5 increases from the inner end 6 to the outer end 7, the contact between the plates within a predetermined rotation speed of the inner end 6 is achieved. Can be more reliably prevented.
In the torque characteristics of the spiral spring device 1B, as in the first and second embodiments, the torque at the end of the tightening and the torque at the beginning of the rewinding within the range of the predetermined number of rotations of the inner end 6 are different. The distance between the winding and the rewinding curve is close to each other, and the difference in torque change between the time of winding and the time of rewinding is small. Thus, the range of use such as winding and rewinding can be expanded.

  Although the forcible displacement member 4 is in contact with the 1/4 turn, it is sufficient that the forcible displacement member 4 contacts the vicinity of the 1/4 turn including the 1/4 turn.

[Fourth embodiment]
9 and 10 show a spiral spring device 1C according to a fourth embodiment of the present invention.
Also in this embodiment, in the spiral spring 2, the plate material 5 is spirally wound, and the interval between the plate materials 5 gradually increases from the inside to the outside, so that they are not in contact with each other. The rotating shaft 8 from the device is inserted into the case 3, and the locking pin 9 from the device is inserted into the case 3. The spiral spring 2 is housed in the case 2 with the inner end 6 hooked to the rotating shaft 8 and the outer end 7 hooked to the hooking pin 9. The case 3 is provided with a forced deflection member 4.

The forced deflection member 4 is formed in a thin arc-shaped fin shape and provided in the case 3. The outer peripheral surface 14 of the forcibly displaced member 4 is in contact with the inside of the plate 5 in a region including the 1/4 turn of the spiral spring 2, that is, in the vicinity of the 1/4 turn. It is forcibly displaced radially outward. Since the forced deflection member 4 is formed in a fin shape in this manner, the length of contact with the plate member 5 can be increased, and thus the forced deflection can be performed stably.

FIG. 10 shows the operation of the forced deflection member 4. The forcible deflection member 4 abuts against the region including the quarter-turn portion of the plate material 5 from the inside with respect to the spiral spring 2a before the forced deflection indicated by the dotted line in FIG. The spiral spring 2 is displaced outward in the direction, and becomes a spiral spring 2 in a solid line state. As a result, the entire spiral spring 2 is displaced in the direction of the quarter turn.
Also in this case, the forced displacement by the forced displacement member 4 is performed such that even when the spiral spring 2 is tightened by a predetermined number of rotations of the inner end 6, the adjacent plate members 5 maintain a non-contact state with each other. The forced displacement is adjusted.

  When the rotating shaft 8 rotates clockwise and tightens the spiral spring 2 in such a structure provided with the forced deflection member 4, the quarter turn of the spiral spring 2 is forcedly shifted outward from the beginning. Because of this, there is no deviation in the direction of the 3/4 turn, and in the 1/4 turn portion, the pitch of the plate 5 can be suppressed from becoming dense, and contact between the plates 5 can be prevented. . Thereby, it is possible to prevent generation of abnormal noise and fluctuation of torque characteristics due to contact between plates.

Also in this embodiment, since the spiral spring 2 is wound so that the interval between the plate members 5 increases from the inner end 6 to the outer end 7, the contact between the plates within a predetermined rotation speed of the inner end 6 is achieved. Can be more reliably prevented.
Further, in the torque characteristics of the spiral spring device 1C, as in the first embodiment and the second embodiment, the torque at the end of the tightening and the initial torque at the rewinding within a predetermined rotation speed of the inner end 6 are determined. And the distance between the winding and rewinding curves is close to each other, and the difference in torque change between when tightening and when rewinding is small. And the use range of the tightening and rewinding can be expanded.

1, 1A, 1B, 1C: spiral spring device, 2: spiral spring, 3: case, 4: forced displacement member, 5: plate material, 6: inner end, 7: outer end, 8: rotary shaft, 9: hook Stop pin

Claims (3)

A spiral spring having a non-contact structure in which the interval between the spirally wound plate members gradually increases from the inner end to the outer end;
A case accommodating the spiral spring such that the inner end of the spiral spring is on the rotation side and the outer end is on the fixed side,
A spiral member, wherein the case is provided with a forcible deflection member which abuts on the outside of the plate material in the vicinity of the 3/4 turn from the outer end of the spiral spring to forcibly deviate the plate material inward in the radial direction. Spring device. A spiral spring having a non-contact structure in which the interval between the spirally wound plate members gradually increases from the inner end to the outer end;
A case accommodating the spiral spring such that the inner end of the spiral spring is on the rotation side and the outer end is on the fixed side,
A spiral member, wherein a forced displacement member is provided in the case to abut the inside of the plate material in the vicinity of the quarter turn from the outer end of the spiral spring to forcibly deviate the plate material radially outward. Spring device. 3. The forced displacement member according to claim 1, wherein the forced displacement member performs a forced displacement such that adjacent plate members maintain a non-contact state with each other when the spiral spring is tightened by rotation of the inner end. Spiral spring device.

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