JPH08296683A - Damping device - Google Patents

Abstract

PURPOSE: To generate frictional force between frictional plates for attenuating rotational speed of a rotation side member by composing a device of a first frictional plate, second and third frictional plates arranged so as to sandwich it, a plate spring, and a cam, and thereby coping with a rotational angle for generating a large torque on the rotation side member. CONSTITUTION: Either one of a unit of a first frictional plate 7 and a first bracket 17 and a unit of a shaft 6, second and third frictional plates 8, 9 and a second bracket 18 is fixed, while the other is connected to a rotation side member. When the rotation side member is rotated, the unit connected therewith is also rotated. The rotational speed of the rotation side member is attenuated due to frictional force generated between the first frictional plate 1 and the frictional plates 8, 9. Shock caused by high speed rotation of the member is thus attenuated. When a rotational angle is generated on the rotation side member for generating a large torque, a plate spring 11 is further pressurized in the direction for pressing the second and third frictional plates 8, 9 against the first frictional plate 7 by means of a cam 14 correspondingly to the rotational angle.

Description

Detailed Description of the Invention

[0001]

The present invention relates to a reclining seat for vehicles, a theater seat of a type in which a seat cushion is flipped up, a door closer, a trunk of an automobile, a piano or an electone door, etc. Regarding the device.

[0002]

2. Description of the Related Art As a conventional technique of a loosening device incorporated in a reclining device, for example, Japanese Patent Laid-Open No. 1-107708.
There is a technique described in the publication, and this conventional technique is shown in FIG.

A reclining unit 20, which is a loosening device shown in FIG. 20, has a stationary member A and a rotating member B.
It is configured by combining and.

The fixed member A is a connecting plate 21.
And the fin receiving plate 22 and the connecting plate 21.
And a plurality of fixed fins 23 such as four interposed between the fins and the fin receiving plate 22, and the plurality of fixed fins 23.
And a set screw 24 that connects the connection plate 21 and the fin receiving plate 22 to each other.

The rotating member B is a lever plate 25.
And a low-profile sleeve-shaped fin receiving plate 26
And 5 pieces which are arranged on both sides of the fixed fin 23 and are accommodated in the fin receiving plate 26,
A plurality of rotating fins 27 and the fin receiving plate 2
6 and the cap plate 28, and the rotary fin 2
It is composed of a lever plate 25 for accommodating seven, a fin receiving plate 26, and a rivet 30 connecting three members of a cap plate 28.

A circular step portion 23 'is formed on the fixed fin 23, and a circular step portion 27' is formed on the rotary fin 27, and the rotary fin 27 and the fixed fin 23 are alternately laminated. A predetermined clearance can be secured between both fins.

Viscous grease 29 is filled in the clearance formed between the fixed fin 23 and the rotary fin 27 and the clearance between the rotary fin 27 and the cap plate 28.

Then, the reclining unit 20
Is provided between the base bracket fixed to the side portion of the seat cushion of the reclining seat and the arm bracket fixed to the side portion of the seat back. That is, the reclining unit 2 is attached to the shaft body protruding to the side portion of the base bracket fixed to the seat cushion side.
The connection plate 21 of the fixed member A of No. 0 is engaged and connected. Further, the lever plate 25 of the rotation side member B of the reclining unit 20 is attached to the arm bracket fixed to the seat back side.

By the way, in the reclining seat, when the seat back is erected from the most tilted position to the rear, the restoring force is the largest and may give a shock to the seated person.

On the other hand, in the reclining unit 20 shown in FIG. 20, when the seat back is rotated in the standing direction from the most tilted position to the rear, the clearance between the fixed fin 23 and the rotary fin 27, and the rotary fin. Since the rotational speed of the rotary fins 27 is reduced by the shearing force of the viscous grease 29 enclosed in the clearance between the cap sheet 28 and the cap plate 28, the seat back stands up at a slow speed. Moreover, the viscous grease 2
Since the shearing force of 9 increases as the rotational speed of the seat back increases, abrupt rotation of the seat back in the upright direction can be suppressed and the impact can be mitigated.

Further, as a damper device for a cassette lid which is attached to the housing so as to be openable and closable, it is disclosed in Japanese Utility Model Publication 57-52729.
There is a technique described in Japanese Patent Publication. Further, as a tilt mechanism for rotatably attaching a display panel or the like to the device body and holding the display panel or the like at an arbitrary angle, for example, an actual flat plate 1-1177
There are techniques described in Japanese Patent Application Laid-Open No. 97-97, Japanese Patent Application Laid-Open No. 2-38710.

[0012]

By the way, as shown in FIG.
In the prior art shown in (1), it is necessary to combine a large number of fixed fins 23 and rotary fins 27 in order to obtain a large damper force, and to fill viscous grease 29 between the large number of fins. Fin 2
In order to secure a predetermined clearance between the fixed fins 23 and the rotary fins 27, circular step portions 23 ', 27'
However, there is a problem that the structure is complicated and the size becomes large. Further, in the conventional technique shown in FIG. 20, the damper force is uniquely determined by the shearing force of the viscous grease 29 enclosed and the clearance between the fixed fin 23 and the rotary fin 27, and there is a problem that the damper force cannot be adjusted. .

Further, the above-mentioned Japanese Utility Model Publication No. 57-52729, Japanese Utility Model Publication No. 1-117797 and Japanese Patent Application Laid-Open No. 2-3.
The conventional technique described in Japanese Patent No. 8710 also has a problem that the structure becomes complicated and the size and cost of the device cannot be avoided.

An object of the present invention is to solve the above-mentioned problems of the prior art, and to generate a frictional force between the friction plates that attenuates the rotational speed of the rotating side member in accordance with the rotation angle at which a large torque is generated in the rotating side member. An object of the present invention is to provide a slow motion device that can be achieved, and that can drastically simplify the structure, reduce the thickness, and reduce the cost.

Another object of the present invention is to provide a slow motion device capable of properly and reliably adjusting the damper force of the slow motion device.

[0016]

In order to achieve the above-mentioned object, in the present invention, the first friction plate is sandwiched between the first and second friction plates, and the first friction plate A leaf spring that presses the second and third friction plates against the plate is provided, corresponding to the rotation angle at which a large torque is generated in the rotation-side member,
The first friction plate is provided with a cam for pressing a leaf spring in a direction in which the second and third friction plates are pressed, and the first friction plate is attached to the first friction plate.
Attached to the second bracket, and the second and third friction plates are linked to the second bracket via the shaft, the unit of the first friction plate and the first bracket, the shaft, the second and third units. One of the friction plate and the unit of the second bracket is fixed, and the other is connected to the rotary member.

In order to achieve the above object, in the present invention, as the leaf spring, a disc spring, a thin leaf spring, or a fastener spring having an outer shape of a circle or a tooth is used.

In order to achieve the above object, the present invention is provided with an adjusting means for adjusting the spring load of the leaf spring.

[0019]

In the present invention, the first and second friction plates are arranged on one shaft with the first and second friction plates interposed therebetween. The first
Leaf springs for pressing the second and third friction plates against the friction plate. A cam that presses a leaf spring that presses the second and third friction plates is provided on the first friction plate in correspondence with the rotation angle at which a large torque is generated in the rotating member. Attaching the first friction plate to the first bracket,
The third friction plate is linked to the second bracket via the shaft. Then, one of the unit of the first friction plate and the first bracket, the shaft, the unit of the second and third friction plates and the second bracket is fixed,
The other is connected to the rotary member.

In the present invention having such a configuration, when the rotation side member is released from the restraint and the rotation side member rotates, the first friction plate and the first bracket unit or the shaft connected to the rotation side member One of the units of the second and third friction plates and the second bracket rotates with respect to the other. At this time, the leaf springs cause the second and third friction plates to move to the first
Since it is urged in the direction that it is pressed against the friction plate of
The frictional force generated between the first friction plate and the second and third friction plates attenuates the rotation speed of the unit connected to the rotation-side member, and thus the impact due to the rotation-side member rotating at high speed is reduced. Can be relaxed.

Further, when the rotation side member reaches a rotation angle which produces a large torque, that is, when the latch is released with the seat back of the reclining seat tilted to the maximum extent, the rotation angle corresponds to the rotation angle. Then, the cam causes the leaf spring to be further pressed in the direction in which the second and third friction plates are pressed against the first friction plate. Therefore, when a rotation angle at which a large torque is generated in the rotation-side member is reached, the frictional force between the friction plates can be correspondingly increased and the rotation speed of the rotation-side member can be damped.

Further, according to the present invention, the slow-moving portion is constituted by the first friction plate, the second and third friction plates arranged on both sides of the first friction plate, the leaf spring, and the cam. The structure can be greatly simplified, it can be made extremely thin, the number of parts is small, and the number of manufacturing and assembling steps for each member can be reduced, resulting in a significant cost reduction.

Further, in the present invention, a disc spring is used as the leaf spring,
A thin leaf spring or a fastener spring with a circular or toothed outer shape is selected and used. With this, it is possible to surely reduce the thickness of the slow motion portion by using the leaf spring having an appropriate spring load.

In the present invention, the adjusting means for adjusting the spring load of the leaf spring is provided. Therefore, the spring load of the leaf spring can be accurately adjusted by the spring load adjusting means, and thereby the frictional force between the first friction plate and the second and third friction plates can be properly and reliably adjusted. .

[0025]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a perspective view showing an example of a reclining seat to which the loosening device of the present invention is attached.

The reclining seat shown in FIG. 1 is
A seat cushion 1, a seat back 2, and a reclining mechanism are provided. The reclining mechanism is
The seat cushion 1 is configured to have a base bracket 3 attached to a side surface of the seat cushion 1 and an arm bracket 4 attached to the seat back 2 and pivotally supported by the base bracket 3. 1
It is designed to be used by tilting it in the direction of arrow a.

When the rack (not shown) is removed with the seat back 2 tilted to the maximum extent, the torque of the return spring (also not shown) becomes the largest,
Therefore, the seat back 2 rotates in the upright direction at a high speed. Therefore, in order to suppress the sudden rotation of the seat back 2,
The loosening device 5 is attached.

2 to 18 show an embodiment of the present invention. FIG. 2 is a partially cutaway front view of the loosening device, FIG. 3 is a left side view of FIG. 2, and FIG. 4 is a right side of FIG. FIG. 5 is a front view of the shaft, FIG. 6 is a right side view of FIG. 5, FIG. 7 is a front view of a unit of the first friction plate and the first bracket, and FIG. 8 is a left side view of FIG. 9 is a side view of the second and third friction plates, FIG. 10 is a vertical sectional front view of a disc spring that is a plate spring, FIG. 11 is a right side view of FIG. 10, and FIG. 12 is a side view of a cam support plate. 13 is a vertical sectional front view of the cam, FIG. 14 is a right side view of FIG. 13, FIG. 15 is a side view showing the cam surface, FIG. 16 is a developed view of the cam surface, and FIG. 17 is a second view.
18 is a front view of the bracket of FIG. 18, and FIG. 18 is a right side view of FIG.

The loosening device 5 of the embodiment shown in these figures is
As shown in FIGS. 2 to 4, the shaft 6, the first, second and third friction plates 7, 8 and 9 and the disc spring 1 which is a plate spring.
1, a cam support plate 13, a cam 14, and a lock nut 1
6 and first and second brackets 17 and 18 are provided.

In this embodiment, as shown in FIGS. 5 and 6, the shaft 6 is formed in a substantially oval shape in which both sides in the diametrical direction are cut. A male screw 6'is formed at the end of the shaft 6 on the second friction plate 8 side.

As shown in FIG. 8, the first friction plate 7 has a circular hole formed in the center thereof so as to fit into the outer shape of the shaft 6, and the first friction plate 7 has the hole. It is loosely fitted to the shaft 6 via. Also, the first friction plate 7
As shown in FIGS. 7 and 8, holders 12 for the cam support plates are provided on the outer periphery of the cam support plate at two locations in the diametrical direction.

The second and third friction plates 8 and 9 are shown in FIG.
As shown in FIG. 5, an oval-shaped hole is formed in the center portion like the outer shape of the shaft 6. And the second and third
The friction plates 8 and 9 are tightly fitted to the shaft 6 through the holes, are arranged on both sides of the first friction plate 7 and can be frictionally contacted with each other.

A lubricant 10 is applied between the first friction plate 7 and the second friction plate 8 and between the first friction plate 7 and the third friction plate 9, respectively. .

The disc spring 11 is formed in the shape shown in FIGS. This disc spring 11 is arranged outside the third friction plate 9 through the shaft 6,
The second and third friction plates 8 and 9 are pressed against the first friction plate 7 in a frictionally contacting direction.

As shown in FIG. 12, the cam support plate 13 is formed in an elongated shape having a ring-shaped portion 13a and rectangular portions 13b and 13b extending in the diameter direction thereof. Inside the ring-shaped portion 13a, a plurality of protrusions 13c such as four are provided at regular intervals in the circumferential direction. The rectangular portion 13b,
The outer end of 13b is formed with hooking grooves 13d and 13d which fit into holders 12 and 12 provided at two positions on the outer side of the first friction plate 7, respectively. ，
It is hung and supported by the holders 12 and 12 via 13d.

As shown in FIGS. 13 to 15, the cam 14 has a circular hole formed in the center thereof so as to fit into the outer shape of the shaft 6. Further, as shown in FIG. 14, the cam 14 has a protrusion 13c provided on a ring-shaped portion 13a of the cam support plate 13 at a constant interval in the circumferential direction.
An engaging groove 14a that engages with is formed. Further, on the end surface of the cam 14 on the side opposite to the disc spring 11, cam surfaces are formed at intervals of 180 ° in the circumferential direction.
As shown in FIG. 14 and FIG. 15, each cam surface is composed of a gentle slope 15a, a flat surface 15b following it, a steep slope 15c following it, and a flat surface 15d following it. The range of use is shown by the symbol L in FIG. Then, the cam 14 is loosely fitted to the outside of the shaft 6 through a hole formed in the central portion, and the protrusion 13c provided inside the ring-shaped cam support plate 13 and the engagement groove formed in the cam 14 are provided. Supported by the cam support plate 13 through engagement with 14a,
It is mounted between the disc spring 11 and the second bracket 18, and is rotated twice at an interval of 180 ° for each rotation of the rotary side member. The disc spring 11 can be pressed in the direction in which 9 is pressed.

The lock nut 16 is screwed into a male screw 6'formed on one end of the shaft 6. The disc spring 11 is formed by the male screw 6 ′ and the lock nut 16.
It constitutes an adjusting means for adjusting the spring load of the.

As shown in FIGS. 7 and 8, the first bracket 17 is formed in an L-shape, and the first friction plate 7 is formed.
It is formed integrally with.

As shown in FIGS. 17 and 18, the second bracket 18 is formed in a shape having a disc-shaped portion 18a and rectangular portions 18b, 18b extending in the diameter direction thereof. Has been done. The disk-shaped portion 18a
Includes two projections 18c that support the cam 14 from the back,
Two screw holes are provided. A hooking groove 18d for connecting to another member is formed at the outer end of each rectangular portion 18b. The second bracket 18 is joined to the other end of the shaft 6 by a screw 19.

In this embodiment, the unit of the first friction plate 7 and the first bracket 17 is attached to the side portion of the seat back 2 of the reclining seat shown in FIG. 1 via the first bracket 17. It rotates in synchronization with the seat back 2. On the other hand, the unit of the shaft 6, the second and third friction plates 8 and 9, and the second bracket 18 is attached and fixed to the side portion of the seat cushion 1 of the reclining seat via the second bracket 18. ing.

Next, the operation of the loosening device 5 of the above embodiment will be described.

As described above, the unit of the first friction plate 7 and the first bracket 17 is attached to the seat back 2 of the reclining seat, and the shaft 6, the second and third friction plates 8 and 9 and the second bracket are attached. In a use state in which the unit 18 is fixed to the side portion of the seat cushion 1 of the reclining seat, the unit of the first friction plate 7 and the first bracket 17 rotates together with the seat back 2. In this embodiment, the holder 12 provided on the first friction plate 7
Since the cam 14 is attached via the cam support plate 13 which is hooked on the cam 14, the cam 14 also rotates around the shaft 6 together with the first friction plate 7.

By the way, when the seat back 2 is tilted to the maximum rearward, the torque of the return spring of the reclining mechanism becomes maximum. In this state, remove the latch and push the seat back 2 forward.
May rotate at a high speed and may give an impact to a seated person.

Therefore, in this embodiment, the cam 14 shown in FIG.
The disc spring 11 is strongly pressed near the steep slope 15c of the cam surface shown in FIG. When the disc spring 11 is strongly pressed by the cam 14 and the amount of deflection increases, the second and third friction plates 8 and 9 are strongly pressed against the first friction plate 7. As a result, the frictional force between the first friction plate 7 and the second and third friction plates 8 and 9 increases, and the rotation speed of the first friction plate 7 is attenuated,
The rotation speed of the seatback 2 is suppressed via the first bracket 17, the torque is reduced, and the impact given to the seated person is alleviated.

As the seat back 2 approaches the upright state, the torque due to the action of the return spring becomes smaller. In this state, the pressing force of the disc spring 11 by the cam 14 which rotates together with the first friction plate 7 is gradually reduced to reduce the amount of deflection of the disc spring 11 to reduce the first friction plate 7 and the second friction plate 7. The frictional force between the friction plates 8 and 9 of 3 is reduced.

Therefore, in this embodiment, the rotational speed of the seat back 2 can be averaged, and the seated person can be given a sense of security.

FIG. 19 is a graph showing the relationship between the rotation angle of the seat back of the reclining seat and the torque, and the characteristics of the loosening device of the present invention.

In this FIG. 19, T1 is the required torque, T2 is the friction torque by the slackening device of the present invention,
T3 represents the torque when the deflection amount of the disc spring is adjusted to a certain value. ΔT is the torque difference between T1 and T2,
The torque difference ΔT determines the speed at which the seat back returns.

Further, in this embodiment of the present invention, as shown in FIGS. 2 and 4, a screw 6'is formed on one end of the shaft 6, and a lock nut 16 is fitted to this. By tightening or loosening the lock nut 16 and adjusting the spring load of the disc spring 11, the frictional force between the first friction plate 7 and the second and third friction plates 8 and 9 is properly and reliably adjusted. be able to. When applied to a reclining seat, even if the reference torque of the return spring changes, the lock nut 16 causes the disc spring 11 to move.
This can be easily dealt with by adjusting the amount of deflection.

Further, according to this embodiment, the slow-moving portion is provided with the first friction plate 7 and the second and third friction plates arranged on both sides thereof.
Friction plates 8 and 9, a disc spring 11 which is a leaf spring, and a cam 1.
4, the width W of the loosening device 5 can be made extremely thin, as can be seen from FIG.

In the present invention, the lock nut 16 may be omitted depending on the specifications of the member on which the loosening device 5 is incorporated.
The second friction plate 8 may be directly attached to one end of the shaft 6 with a screw or the like.

Further, in the present invention, the leaf spring is not limited to the disc spring 11, but a thin leaf spring may be used, or a fastener spring or the like having a circular outer shape or a tooth shape may be used.

The unit of the first friction plate 7 and the first bracket 17 is attached to the fixed member, and the unit of the shaft 6, the second and third friction plates 8 and 9 and the second bracket 18 is rotated. You may make it attach to a side member and use it.

Further, the loosening device 5 according to the present invention can be applied not only to the reclining seat but also to the following uses. (1) Theater seats of the type that flips up the seat cushion (2) Doors for underfloor storage (3) Doors for piano, electone, etc. (4) Car trunks (5) Door closers

[0056]

As described above, according to the first aspect of the present invention.
According to the invention described above, the second and third friction plates are arranged on one shaft with the first friction plate interposed therebetween, and the second and third friction plates are arranged with respect to the first friction plate. And a cam for pressing the leaf spring in a direction to press the second and third friction plates against the first friction plate in accordance with a rotation angle at which a large torque is generated in the rotary member. A first friction plate is attached to the first bracket, second and third friction plates are linked to a second bracket via the shaft, and the first friction plate and the first bracket unit are connected to each other; One of the shaft, the second and third friction plates, and the unit of the second bracket is fixed, and the other is connected to the rotation side member, so that the rotation side member is released from the restraint and the rotation side member is released. When the rotating member rotates, the first friction plate and the first bracket connected to the rotating member are Of the shaft, the shaft, the second, third friction plates, and the second bracket unit rotate with respect to the other, the leaf springs cause the second and third friction plates to contact each other. Since it is urged in the direction of being pressed against the plate, the frictional force generated between the first friction plate and the second and third friction plates attenuates the rotational speed of the unit connected to the rotary side member, thus There is an effect that the impact due to the rotation side member rotating at a high speed can be alleviated, and when the rotation side member reaches a rotation angle that produces a large torque, the cam causes the leaf spring to move in correspondence with the rotation angle. Since the pressure is further applied in the direction in which the second and third friction plates are pressed against the first friction plate, when there is a rotation angle at which a large torque is generated in the rotation side member, the friction plates are correspondingly moved between them. Increase the frictional force of There is an effect that the rotation speed of the rotation side member can be attenuated, and further, the slow motion portion is provided with the first friction plate, the second and third friction plates arranged on both sides of the first friction plate, the leaf spring, and the cam. Because it is configured by
The structure can be greatly simplified, it can be made extremely thin, the number of parts is small, and each member can be manufactured.
Since the number of assembling steps can be reduced, there is also an effect that the cost can be significantly reduced.

According to the second aspect of the present invention, as the leaf spring, a disc spring, a thin leaf spring, or a fastener spring having a circular or toothed outer shape is used, so that an appropriate spring load is applied. There is an effect that the slow-moving portion can be surely thinned by using the leaf spring.

Further, since the adjusting means for adjusting the spring load of the leaf spring is provided, the spring load of the leaf spring can be accurately adjusted by the adjusting means of the spring load, whereby the first friction plate and the second friction plate can be adjusted. There is an effect that the frictional force between the third friction plates can be properly and surely adjusted.

[Brief description of drawings]

FIG. 1 is a perspective view showing a reclining seat to which the present invention is applied.

FIG. 2 shows an embodiment of the present invention and is a partially cutaway front view of the loosening device.

FIG. 3 is a left side view of FIG.

FIG. 4 is a right side view of FIG.

FIG. 5 is a front view of a shaft.

FIG. 6 is a right side view of FIG.

FIG. 7 is a front view of a unit of a first friction plate and a first bracket.

FIG. 8 is a left side view of FIG.

FIG. 9 is a side view of second and third friction plates.

FIG. 10 is a vertical sectional front view of a disc spring which is a leaf spring.

11 is a right side view of FIG.

FIG. 12 is a side view of a cam support plate.

FIG. 13 is a vertical sectional front view of a cam.

FIG. 14 is a right side view of FIG.

FIG. 15 is a side view showing a cam surface.

FIG. 16 is a development view of a cam surface.

FIG. 17 is a front view of a second bracket.

FIG. 18 is a right side view of FIG.

FIG. 19 is a graph showing the relationship between the rotation angle and torque of the seat back of the reclining seat to which the present invention is applied, and the characteristics of the loosening device of the present invention.

FIG. 20 is a vertical sectional view showing a conventional technique.

[Explanation of symbols]

 5 Loosening Device 6 Shaft 7 First Friction Plate 8 Second Friction Plate 9 Third Friction Plate 11 Disc Spring 14 Cam 6'Male Screw 16 Lock Nut 17 First Bracket 18 Second Bracket

Claims (3)

[Claims] 1. A single shaft is provided with second and third friction plates sandwiching a first friction plate, and the second and third friction plates are pressed against the first friction plate. A leaf spring is provided, and a cam is provided to press the leaf spring in a direction in which the first and second friction plates are pressed against the first friction plate in accordance with a rotation angle at which a large torque is generated in the rotation side member. Friction plate is attached to the first bracket, the second and third friction plates are linked to the second bracket via the shaft, the unit of the first friction plate and the first bracket, and the shaft And a second friction plate, a second bracket unit, or a second bracket unit, and the other unit is connected to a rotary member. 2. A leaf spring, a thin leaf spring,
The loosening device according to claim 1, wherein a fastener spring having a circular outer shape or a tooth shape is used. 3. The loosening device according to claim 1, further comprising adjusting means for adjusting a spring load of the leaf spring.