JPH10311359A - Rotary damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary damper wherein desired braking force can be obtained from the initial stage of braking. SOLUTION: A device comprises a casing 1 provided with a guide shaft 3, slider 21 provided with an orifice partitioning inside the casing 1 into two chambers Ra, Rb to make communication thereof, coil spring 11 energizing the slider 21 to the side of a cap 5 constituting the casing 1, O ring 31 arranged between the guide shaft 3 and the slider 21, V ring 41 arranged between a casing main unit 2 and the slider 21, rotor 51 wherein a shaft part 55 protrudes from a support shaft hole 6 of the cap 5, O ring 61 arranged between the cap 5 and the shaft part 55, and silicone oil 81 with which the chambers Ra, Rb are charged. Between the slider 21 and the rotor 51, a cam mechanism is provided, which, by rotating the rotor 51, moves the slider 21 along the guide shaft 3 against energizing force of the coil spring 11.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary damper for gently opening a lid of a glove compartment of an automobile or opening a lid covering a front surface of an operation panel of an audio product. is there.

[0002]

2. Description of the Related Art As a conventional rotary damper, a ratchet mechanism is provided for giving directionality to a braking force of a rotor. When the rotor rotates in a direction in which the ratchet mechanism meshes, a viscous fluid is applied to the rotational force of the rotor. For example, Japanese Utility Model Laid-Open No. 6-45047 discloses a configuration in which a braking force is applied by viscous resistance, and when the rotor rotates in a direction in which the ratchet mechanism slides, no braking force is applied to the rotation of the rotor.

[0003]

The above-mentioned conventional rotary damper has a configuration in which a braking force (braking torque) is obtained by following the rotation of the rotor, and the rotor follows the rotation of the rotor at an early stage of braking. There is a disadvantage that the braking force cannot be obtained.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned disadvantages, and it is an object of the present invention to provide a rotary damper capable of obtaining a desired braking force from an initial braking period.

[0005]

A rotary damper according to the present invention has a casing provided with a guide shaft in the axial direction at the center of the bottom, and a shaft hole provided at a position of the ceiling corresponding to the guide shaft. The casing is movably accommodated in the casing along the guide shaft to partition the casing into two chambers.
A slider provided with an orifice communicating the two chambers,
A biasing member for biasing the slider toward the ceiling of the casing, and a rotor which is housed in the casing with a flange positioned between the ceiling of the casing and the slider, and the shaft of which projects from a shaft hole of the casing. A sealing member that enables the shaft of the rotor to rotate with respect to the ceiling of the casing, and seals the space between the ceiling and the shaft in a water-tight manner, and a viscous fluid filled in the two chambers. A cam mechanism is provided between the rotor and the rotor to move the slider along the guide shaft against the urging force of the urging member when the rotor rotates.

An elastic deformation ring for forming a viscous fluid flow path only when the slider moves in one direction is provided between the inner periphery of the casing and the outer periphery of the slider, or the slider is provided with respect to the guide shaft. Is desirably provided with a sealing member that enables sliding between the guide shaft and the slider.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is an exploded perspective view of a rotary damper according to a first embodiment of the present invention, and FIGS. 2 to 4 are operation explanatory diagrams of the first embodiment. The V-ring in FIG. 1 is partially cut away, and FIGS. 2 to 4 correspond to cross-sectional views taken along line AA of the slider after assembling the members in FIG.

In these figures, reference numeral 1 denotes a casing, and a casing body 2 having a cylindrical shape with a bottom made of synthetic resin.
And a synthetic resin cap 5 that closes the opening of the casing body 2 to form a ceiling.
The casing main body 2 is provided with a guide shaft 3 having an oval horizontal cross section at the center of the bottom, and a housing groove 4 circulating at the upper end of the peripheral wall. Also, the cap 5
A circular support hole 6 is provided at a corresponding position on the extension of the guide shaft 3.
Is provided, and a stepped portion 7 is provided around the lower portion of the shaft hole 6.
Is provided.

Reference numeral 11 denotes a coil spring as an urging member, which is housed in the casing 1 so as to be positioned around the guide shaft 3 of the casing main body 2 and urges a slider 21 described later toward the cap 5 of the casing 1. Is what you do.

Reference numeral 21 denotes a slider made of synthetic resin, which has a cylindrical shape having a ceiling and is housed in the casing 1. The slider 21 is provided at the center of the ceiling with an insertion hole 22 which is substantially the same as the horizontal cross section of the guide shaft 3 of the casing main body 2 and has an orbiting accommodation groove 23. Two first cams 24 having the first cam surfaces 25 descending are provided at 180 degrees on the same circumference. Further, the slider 21 is provided with an orifice 26 that communicates the inside and the outside with the ceiling, and a housing groove 27 that circulates in a lower part on the outside.

Reference numeral 31 denotes an O-ring as a sealing member,
The slider 21 is disposed in the housing groove 23 of the slider 21 and is slidable with respect to the guide shaft 3 of the casing body 2.
The space between the guide shaft 3 and the ceiling of the slider 21 is sealed in a watertight manner. Reference numeral 41 denotes a V-ring as an elastically deformable ring, which is disposed in the accommodation groove 27 of the slider 21 and watertightly seals between the inner periphery of the casing main body 2 and the outer periphery of the slider 21, A viscous fluid flow path is formed between the circumference and the outer circumference of the slider 21.

Numeral 51 denotes a synthetic resin rotor, which is a flange 52 having a circular planar shape accommodated in the casing 1.
A second cam surface 54 provided on the same circumference below the flange portion 52 in correspondence with the two first cam surfaces 25 of the slider 21 and sequentially descending clockwise at a constant rate. It comprises two second cams 53 and a shaft portion 55 projecting upward from the center of the flange portion 52 and projecting from the support hole 6 of the cap 5.

Reference numeral 61 denotes an O-ring as a sealing member,
The shaft portion 55 of the rotor 51 is rotatable with respect to the cap 5, and is provided on the step portion 7 of the cap 5 to seal the gap between the cap 5 and the shaft portion 55 in a watertight manner. Reference numeral 71 denotes an O-ring as a sealing member, which is disposed in the housing groove 4 of the casing main body 2 and seals a gap between the casing main body 2 and the cap 5 in a watertight manner. 81 denotes a silicone oil as a viscous fluid, Ra and Rb denote chambers in the casing 1 partitioned by the slider 21, and the chambers Ra and Rb communicate with each other through the orifice 26 of the slider 21.

Note that the outer diameter of the slider 21 and the outer diameter of the rotor 51 are the same. The inner diameter of the casing body 2 is slightly larger than the outer diameters of the slider 21 and the rotor 51. The radial width of the first cam surface 25 and the radial width of the second cam surface 54 are the same. The cam mechanism according to the first embodiment includes:
It is composed of a first cam 24 and a second cam 53.

Next, an example of assembly will be described. First, a predetermined amount of silicone oil 8 is placed in the casing body 2.
After injecting 1, the coil spring 11 is inserted into the casing main body 2 so as to be located around the guide shaft 3.
Next, the O-ring 31 is arranged in the accommodation groove 23, and the insertion hole 22 of the slider 21 in which the V-ring 41 is arranged in the accommodation groove 27 so that the cross-sectional shape becomes an inverted V-shape is turned up, The slider 21 is inserted into the casing body 2.

Then, the second cam surface 54 is connected to the first cam surface 25.
After the rotor 51 is put on the slider 21 corresponding to the above, the O-ring 71 is disposed in the accommodation groove 4, and the O-ring 61 is
The shaft portion 55 is inserted through the shaft hole 6 of the cap 5 disposed in
The cap 5 is brought into contact with the flange 52. In this state, while pressing the cap 5 toward the casing body 2 and slowly rotating the shaft portion 55 clockwise in FIG.
The second cam 53 meshes with the first cam 24 and the slider 21
Also rotates.

When the insertion hole 22 coincides with the guide shaft 3, the silicone oil 81 is pressurized by the guide shaft 3 protruding into the insertion hole 22 and being pressed into the O-ring 31 while reducing the coil spring 11. And a chamber R passing between the inner periphery of the casing body 2 and the outer periphery of the slider 21.
a, the silicone oil 81 tries to flow into the chamber Rb, but the silicone oil 81 expands the V-ring 41 and presses against the inner circumference of the casing main body 2.
Cannot flow from the chamber Ra to the chamber Rb through the gap with the outer periphery of the chamber.

The silicone oil 81 passes from the chamber Ra to the chamber Rb through the space between the guide shaft 3 and the ceiling of the slider 21.
However, since the O-ring 61 blocks the flow of the silicone oil 81, the silicone oil 81 in the chamber Ra flows into the chamber Rb only through the orifice 26. When a part of the silicone oil 81 in the chamber Ra flows into the chamber Rb in this manner, the air and the excess silicone oil 81 are discharged out of the casing 1 to a state shown in FIG. , Rb, the assembly is completed by heat welding the casing body 2 and the cap 5.

Next, the operation will be described. First, FIG.
When the shaft portion 55 is rotated counterclockwise in FIG. 1 in the state shown in FIG.
Are engaged to prevent the rotation, only the rotor 51 rotates counterclockwise, and the second cam surface 54 is
5, the slider 21 is pressed down against the urging force of the coil spring 11. When the slider 21 is depressed in this manner, as described above, the chamber Ra
Since the silicone oil 81 flows into the chamber Rb only through the orifice 26, a braking force is generated by the flow path resistance of the orifice 26 until the state shown in FIG.

Next, in the state of FIG. 3, when the shaft portion 55 is rotated clockwise in FIG. 1, the second cam surface 54 slides down the first cam surface 25. It rises by the force, and the silicone oil 81 in the chamber Rb is pressurized. When the slider 21 moves up and the silicone oil 81 in the chamber Rb is pressurized, the pressurized silicone oil 81 is
By pressing and deforming as shown in FIG. 4, a flow path is formed between the inner periphery of the casing main body 2 and the outer periphery of the slider 21, so that the silicone oil 81 in the chamber Rb is filled with the orifice 26 and the casing main body 2 Inner circumference and slider 2
1 and flows into the chamber Ra, so that the braking force due to the flow path resistance of the orifice 26 is not generated until the state shown in FIG.

As described above, according to the first embodiment of the present invention, since the braking force is applied by the flow path resistance of the orifice 26, the desired braking force can be obtained from the initial stage of braking. Then, the first and second cam surfaces 25, 54
By changing the inclination angle of the slider 21, the moving speed of the slider 21 can be changed.
, The braking force can be made different.

Further, a V-ring 41 for forming a flow path of the silicone oil 81 is provided between the inner periphery of the casing body 2 and the outer periphery of the slider 21 only when the slider 21 moves in one direction. Power can be given direction. Furthermore, since the O-ring 61 is disposed between the guide shaft 3 and the slider 21, the silicone oil 81 when applying a braking force flows only through the orifice 26, so that a large braking force can be easily obtained. .

The O-ring 31 and the V-ring 41
Is provided, there may be gaps between the guide shaft 3 and the slider 21 and between the inner circumference of the casing body 2 and the outer circumference of the slider 21, so that the dimensional accuracy of the casing body 2 and the rotor 51 is relaxed. It can be easily manufactured.

FIG. 5 is a side view of a slider and a rotor used in a rotary damper according to a second embodiment of the present invention. The same or corresponding parts as in FIGS. . In FIG. 5, reference numeral 21A denotes a slider made of a synthetic resin, and two cams 24A having a cam surface 25A which descends gently in a clockwise direction and then descends sharply upward are provided on the same circumference by 180 degrees each. .

Reference numeral 51A denotes a rotor made of synthetic resin, and two cam surfaces 25 of the slider 21A are provided below the flange 52.
A two drive rods 53A are provided in the axial direction at intervals of 180 degrees on the same circumference corresponding to A. The slider 21A is provided with an insertion hole 22, accommodation grooves 23 and 27, and an orifice 26, as in the first embodiment.

FIG. 6 is a side view of a slider and a rotor used in a rotary damper according to a third embodiment of the present invention. The same or corresponding parts as in FIGS. . In FIG. 6, reference numeral 21B denotes a slider made of a synthetic resin, and two cams 24B having a cam surface 25B which descends gently after abruptly descending clockwise upward are provided on the same circumference by 180 degrees. . In addition, as in the first embodiment, the insertion holes 22 and
Housing grooves 23 and 27 and an orifice 26 are provided.

Even if the cam mechanism is configured as shown in FIG. 5 or 6, it can be assembled in the same manner as in the first embodiment.
By configuring the cam mechanism as shown in FIG. 5 or FIG. 6, that is, by connecting two cam surfaces having different inclination angles in succession to form one cam surface 24A, 24B,
Since the moving speed of the sliders 21A and 21B for applying the braking force within the moving stroke can be changed, the braking force from the start to the end of the braking can be changed.

In the above-described first embodiment, by reversing the direction of the V-ring 41 or by reversing the directions of the first and second cams 24 and 53, the rotor 51 for applying a braking force is provided. It goes without saying that the direction of rotation can be changed. In the first embodiment, the slider 21 has the first cam surface 25 and the rotor 51 has the second cam surface 25.
Although the cam surface 54 is provided, the first or second cam 24, 53
Of the transmission rod 53 in the second or third embodiment.
With the configuration as shown in A, the braking force can be made different by replacing the slider or the rotor.

Further, in the first embodiment, the cap 5 is fixed to the casing body 2 by welding, but the cap 5 may be fixed to the casing body 2 by another fixing method. Furthermore, it goes without saying that an attachment portion may be provided in a part of the casing 1. Next, in the second and third embodiments, the cam surfaces 24 are provided on the sliders 21A and 21B.
A and 24B are provided, and a driving rod 53A is provided on the rotor 51A. However, the same operation can be performed by providing a driving rod on the slider and a cam surface on the rotor.

In each embodiment, the orifice 26
Is provided on the ceiling of the slider 21, but may be provided at another position as long as the chambers Ra and Rb can communicate with each other. O-ring 3
The O-ring 31 can be omitted if the space between the guide shaft 3 and the slider 21 is substantially watertight and does not affect the braking force. If the space between the circumference and the outer circumference of the slider 21 is almost watertight and does not affect the braking force,
Can be omitted.

Further, the rotation was made within a range of 180 degrees,
The stopper is rotated in the range of 360 degrees, or the stopper is rotated so that the rotor does not rotate more than approximately 180 degrees or approximately 360 degrees.
It may be provided on the slider or the rotor. Further, although the cam mechanism is illustrated in each embodiment, it is needless to say that a cam mechanism having another configuration that functions similarly may be used. Furthermore, although the silicone oil 81 is used as the viscous fluid, the difference in the braking force between high temperature and normal temperature can be reduced by reducing the viscosity of the silicone oil 81.

[0032]

As described above, according to the present invention, the braking force is applied by the flow path resistance of the orifice.
The desired braking force can be obtained from the initial stage of braking. The moving speed of the slider can be changed by changing the inclination angle of the cam surface constituting the cam mechanism, so that the braking force can be made different by replacing the slider or the rotor. In addition, since the moving speed of the slider can be changed by changing the inclination angle within the cam surface constituting the cam mechanism, the braking force from the start of braking to the end of braking can be changed. .

Further, since an elastically deformable ring is formed between the inner periphery of the casing and the outer periphery of the slider to form a flow path for the viscous fluid only when the slider moves in one direction, the braking force is directional. Can be provided. Further, since the sealing member is provided between the guide shaft and the slider, the viscous fluid for applying the braking force flows only through the orifice, so that a large braking force can be easily obtained.

[Brief description of the drawings]

FIG. 1 is an exploded perspective view of a rotary damper according to a first embodiment of the present invention.

FIG. 2 is an operation explanatory diagram of the first embodiment.

FIG. 3 is an operation explanatory diagram of the first embodiment.

FIG. 4 is an operation explanatory diagram of the first embodiment.

FIG. 5 is a side view of a slider and a rotor used for a rotary damper according to a second embodiment of the present invention.

FIG. 6 is a side view of a slider and a rotor used in a rotary damper according to a third embodiment of the present invention.

DESCRIPTION OF REFERENCE NUMERALS 1 casing 2 casing body 3 guide shaft 4 accommodation groove 5 cap 6 support hole 7 step 11 coil spring 21 slider 21A, 21B slider 22 insertion hole 23 accommodation groove 24 first cam 24A, 24B cam 25 first 1 cam surface 25A, 25B cam surface 26 orifice 27 housing groove 31 O-ring 41 V-ring 51, 51A rotor 52 flange 53 second cam 53A drive rod 54 second cam surface 55 shaft 61, 71 O-ring 81 silicone oil Ra, Rb room

Claims (3)

[Claims] A casing provided with a guide shaft in the axial direction at the center of the bottom, and a shaft hole provided at a position of a ceiling corresponding to the guide shaft; and a casing inside the casing movably along the guide shaft. And the inside of the casing is divided into two chambers.
A slider provided with an orifice communicating the two chambers, an urging member for urging the slider toward the ceiling, and a housing accommodated in the casing with a flange positioned between the ceiling and the slider. A rotor having a shaft portion protruding from the shaft hole; a sealing member that allows the shaft portion to rotate with respect to the ceiling, and seals a gap between the ceiling and the shaft portion in a watertight manner; A viscous fluid filled in a chamber, wherein the rotor is rotated between the slider and the rotor to move the slider along the guide shaft against the urging force of the urging member. A rotary damper provided with a cam mechanism. 2. The rotary damper according to claim 1, wherein: between the inner periphery of the casing and the outer periphery of the slider.
A rotary damper, comprising: an elastic deformation ring that forms a flow path of the viscous fluid only when the slider moves in one direction. 3. The rotary damper according to claim 1, wherein the slider is slidable with respect to the guide shaft, and a gap between the guide shaft and the slider is watertightly sealed. A rotary damper comprising a member.