KR20080082474A - Damper - Google Patents

Abstract

A damper is provided to change torque applied to a rotor corresponding to speed of revolution of the rotor by allowing liquid chambers to be connected to each other or deviated from each other depending on speed of revolution. A damper comprises a housing, a plurality of liquid chambers formed in the housing, a body of revolution rotatably and a passage-variable member. The liquid chambers are filled with viscous liquid. The body of revolution is installed in the housing to encounters resistance of viscous liquid. The body of revolution includes a rotor(22) and an eccentric member(20), which eccentrically rotates on a center of a shaft of the rotor. The passage variable member includes a first passage blocking member(30) and a first elastic support member connected to the first passage blocking member. The first passage blocking member rotates by shear force caused by the rotary or fluidity of the viscous liquid.

Description

Damper {DAMPER}

The present invention relates to a damper that applies torque to the rotor.

In a moving body such as a sliding door or a cash dispenser, a damper for braking the moving body may be used, so that the moving body does not move more strongly than necessary. For example, in patent document 1, the torque acting on a rotating shaft is adjusted by changing the passage | path of a viscous fluid according to the rotating direction of the valve member which rotates with a rotating shaft.

In Patent Document 2, the auxiliary chamber is formed separately from the torque generating chamber, and the torque acting on the rotating shaft is varied by opening and closing the leaf spring disposed between the torque generating chamber and the auxiliary chamber in accordance with the rotational direction of the rotating shaft to adjust the flow rate. Let's do it.

That is, these are that the torque is determined in accordance with the rotational direction of the rotating shaft (rotor), and the torque acting on the rotor does not vary in response to the rotational speed of the rotor.

Patent Document 1: Japanese Patent Application Laid-Open No. 10-115338

Patent Document 2: Japanese Patent Application Laid-Open No. 2000-199536

SUMMARY OF THE INVENTION The present invention has been made in view of the above fact, and an object of the present invention is to provide a damper for varying the torque acting on the rotor corresponding to the rotational speed of the rotor.

The invention according to claim 1 is a damper comprising: a housing, a plurality of liquid chambers formed in the housing and filled with a viscous fluid, a rotating body accommodated rotatably in the housing, and receiving resistance from the viscous fluid of the liquid chamber; When the rotational speed of the rotating body is a predetermined value or more, the liquid chambers are in a non-communication state, and when the rotational speed of the rotating body is less than a predetermined value, the flow path for making the liquid chambers in a communication state has a variable stage. do.

In the invention according to claim 1, a plurality of liquid chambers filled with a viscous fluid are formed in the housing. The housing is rotatably housed in the housing, and the rotor receives resistance from the viscous fluid in the liquid chamber.

Then, when the rotational speed of the rotating body is equal to or higher than the predetermined value, the liquid chambers are in non-communication state by the variable flow path. As a result, in the liquid chamber, in addition to the viscous resistance caused by stirring the viscous fluid in the liquid chamber and the shear resistance generated between the viscous fluid and the rotating body which are not stirred when the rotating body rotates, the viscous fluid is compressed in the liquid chamber. As the compressive resistance is generated and the torque acting on the rotating body increases, the damping force by the damper increases.

When the rotational speed of the rotating body is less than the predetermined value, the fluid chambers are in communication with each other by the variable flow path. As a result, in the liquid chamber, the compressive resistance by compressing the viscous fluid in the liquid solution is reduced (including the case where the compressive resistance almost disappears), and the torque acting on the rotating body is reduced, so that the damping force by the damper is reduced. do.

That is, according to invention of Claim 1, the torque acting on a rotating body can be changed corresponding to the rotating speed of a rotating body.

In the damper according to claim 1, the damper according to claim 2 is characterized in that the rotor rotates eccentrically with respect to an axis of the rotor and a rotor to which a rotational force is transmitted from the outside, and the liquid chamber between the housing and the housing. And an eccentric member constituting the air flow path, wherein the flow path variable stage is rotated by a shear force or a flow force of viscous fluid between the liquid chambers when the rotational speed of the rotor is greater than or equal to a predetermined value. Is connected to the first flow path blocking member and the first flow path blocking member makes the first flow path blocking member in a direction opposite to the rotation direction of the rotor, and the rotation speed of the rotor is a predetermined value. When less than, characterized in that it comprises a first holding means for returning the first flow path blocking member to the position where the liquid chambers are in communication with each other.

In the invention according to claim 2, the rotor is provided with a rotor to which rotational force is transmitted from the outside. The rotor is provided with an eccentric member which is eccentrically rotated with respect to the axial center of the rotor, and the eccentric member constitutes a liquid chamber between the housing and the housing.

In addition, the damper includes a first flow path blocking member that rotates by a shear force or a viscous fluid flow force generated between the rotor and the rotor when the rotational speed of the rotor exceeds a predetermined value. The liquid chambers are brought into a non-communication state by the flow path blocking member.

Further, a first gripping means is connected to the first flow path blocking member, and the first flow path blocking member is supported in a direction opposite to the rotational direction of the rotor. When the rotational speed of the rotor is lower than the predetermined value, the first flow path blocking member returns to the position where the liquid chambers communicate with each other.

As described above, when the liquid chambers are in communication with each other by the first flow path blocking member, the viscous resistance caused by the eccentric member stirring the viscous fluid by the rotation of the eccentric member in the liquid chamber and the stirring when the eccentric member rotates. Shear resistance occurs between the viscous fluid and the eccentric member.

When the rotation speed of the rotor is greater than or equal to a predetermined value, the shear flow force or the flow force of the viscous fluid generated between the rotor becomes larger than that of the first fingering means, thereby rotating the first flow path blocking member. Done. As a result, the liquid chambers are brought into a non-communication state.

Therefore, in addition to the viscous and shear resistance caused by the viscous fluid in the liquid chamber, a compression resistance caused by the compression of the viscous fluid in the liquid by the rotation of the eccentric member is added. Therefore, as the torque acting on the rotor increases, the damping force by the damper increases.

When the rotational speed of the rotor is less than the predetermined value, the shear force or the flow force of the viscous fluid generated between the rotor becomes smaller than that of the first fingering means, thereby restoring the first fingering means. . As a result, the first flow path blocking members are returned to their original positions, whereby the liquid chambers are in communication with each other. Therefore, in the liquid chamber, the compressive resistance by the viscous fluid is reduced and the torque acting on the rotor is lowered, whereby the damping force by the damper is reduced.

In the damper according to claim 2, in the damper according to claim 2, the eccentric member has a first trocoid gear shape, and a second trocoid gear shape is formed on an inner circumferential surface of the housing to engage with the first trocoid gear shape. And the liquid chamber is constituted by the first trocoid gear shape and the second trocoid gear shape.

In the invention according to claim 3, the eccentric member has a first trocoid gear shape, and a second trocoid gear shape that engages with the first trocoid gear shape is formed on the inner circumferential surface of the housing. 1 Viscous resistance caused by the movement of the trocoid gear shape, shear resistance generated between the viscous fluid and the gear portion that is not stirred when the gear portion of the upper portion of the first trocoid gear type moves, and the gear portion of the first trocoid gear shape 2 In the process of engaging the gear portion of the trocoid gear portion, torque can be generated to the rotor by the compression resistance caused by the compression of the viscous fluid in the gear portion of the second trocoid gear portion.

In the damper according to claim 1, the damper according to claim 4 is characterized in that the rotor is a rotor to which a rotational force is transmitted from the outside, and a movable member disposed outside the rotor to constitute the liquid chamber. And cam means for converting the rotational force of the rotor into a movement in a direction along the axial direction of the rotor, wherein the flow path variable stage is provided when the rotational speed of the rotor becomes greater than or equal to a predetermined value. And a second flow path blocking member which rotates by a shear force generated between the rotor and the liquid chambers in a non-communication state, and is connected to the second flow path blocking member in a direction opposite to the rotation direction of the rotor. When the second flow path blocking member is supported and the rotational speed of the rotor is less than a predetermined value, the second flow path blocking member is moved to a position where the liquid chambers communicate with each other. Characterized in that configured by a second elastic supporting means for turning.

In the invention according to claim 4, the rotor is provided with a rotor to which rotational force is transmitted from the outside. The outer side of this rotor is provided with the movement member, and this movement member comprises a liquid chamber with a housing. Then, the cam means converts the rotational force of the rotor into linear movement in the direction along the axial direction of the rotor of the moving member.

In this way, by converting the rotational movement of the rotor into linear movement of the moving member, the moving amount of the moving member can be increased with respect to the moving amount of the rotor. That is, the torque acting on the rotor can be increased.

In addition, the damper includes a second flow path blocking member that rotates by a shear force generated between the rotor when the rotational speed of the rotor reaches a predetermined value or more, and the liquid passage is prevented by the second flow path blocking member. The two become non-communicating. Further, a second gripping means is connected to the second flow path blocking member, and the second flow path blocking member is held in the direction opposite to the rotation direction of the rotor. When the rotational speed of the rotor is less than the predetermined value, the second flow path blocking member is returned to the position where the liquid chambers communicate with each other by the second holding means.

In this way, when the liquid chambers are in communication with each other by the second flow path blocking member, the viscous resistance caused by the movement of the moving member by stirring the viscous fluid due to the movement of the moving member in the liquid chamber is not stirred when the moving member moves. Shear resistance occurs between the viscous fluid and the moving member.

When the rotational speed of the rotor is greater than or equal to the predetermined value, the shear force generated between the rotor becomes larger than the holding force by the second holding means, such that the second flow path blocking member rotates. As a result, the liquid chambers are brought into a non-communication state. Therefore, in addition to the viscous and shear resistance caused by the viscous fluid in the liquid chamber, a compression resistance caused by the compression of the viscous fluid in the liquid chamber by the movement of the moving member is added. Therefore, as the torque acting on the rotor increases, the damping force by the damper increases.

Then, when the rotational speed of the rotor is less than the predetermined value, the shear force generated between the rotor becomes smaller than that of the second holding means, thereby restoring the second holding means. As a result, the second flow path blocking member is returned to its original position, whereby the liquid chambers are in communication with each other. Therefore, in the liquid chamber, the compressive resistance by the viscous fluid is reduced and the torque acting on the rotor is lowered, whereby the damping force by the damper is reduced.

In the damper according to claim 4, in the damper according to claim 4, the movable member protrudes from an inner wall of the housing so as to be movable between the column portions for partitioning the liquid chamber. It is formed on the outer circumferential surface, characterized in that it comprises a cam groove of the waveform having a peak and a curved portion in the axial direction of the rotor, and the engaging projection is formed in the movable member and engaged with the cam groove.

In the invention according to claim 5, the movable member is provided so as to be movable between the pillar portions that protrude from the inner wall of the housing and partition the liquid chamber. On the outer circumferential surface of the rotor, a cam groove having a corrugation having a peak and a curved portion in the axial direction of the rotor is formed, and the engaging member is formed with an engaging protrusion engaged with the cam groove. Therefore, when the rotor is rotated, the movable member can be moved along the axial direction of the rotor in accordance with the shape of the cam groove.

In the damper according to claim 4 or 5, the invention according to claim 6 is characterized in that the engaging projection is engaged with the cam groove so that the moving member moves in phase with each other.

In the invention according to claim 6, since the respective moving members are moved in phases with each other, the respective moving members have different positions in the liquid chamber. Therefore, the torque which arises for every liquid chamber can be changed, and the smoothening of the torque which acts on a rotor is attained.

In the damper according to claim 1, the damper according to claim 1 is characterized in that the rotating body is eccentrically connected with respect to the axis center of the rotor in a state in which a rotational force is transmitted from the outside and the central axis is inclined. And a piston member oscillated by the rotation of the electrons, and a piston member formed in the oscillation member and constituting the liquid chamber between the housing, and reciprocating by oscillation of the oscillation member. When the rotational speed of the rotor is more than a predetermined value, the third flow path blocking member and the third flow path blocking member to rotate by the shear force generated between the rotor and the liquid chambers in a non-communication state; Is connected to the second flow path blocking member in a direction opposite to the rotation direction of the rotor, and when the rotation speed of the rotor is less than a predetermined value, the liquid That is configured to include a third elastic supporting means to a position between a communication path state to return the third flow path shut-off member is characterized.

In the invention according to claim 7, the rotor is provided with a rotor to which rotational force is transmitted from the outside, and has a swinging member which is eccentrically connected with respect to the axis center of the rotor with the central axis inclined. Therefore, the rocking member swings by the rotation of the rotor, and the swinging of the rocking member causes the piston member formed on the rocking member to reciprocate. A liquid chamber is comprised between this piston member and a housing.

In this way, by converting the rotational movement of the rotor into the reciprocating movement of the piston member, the movement amount of the piston member can be increased with respect to the movement amount of the rotor. That is, the torque acting on the rotor can be increased.

In addition, the damper includes a third flow path blocking member that rotates by a shear force generated between the rotor when the rotational speed of the rotor reaches a predetermined value or more, and the liquid chamber is closed by the third flow path blocking member. The two become non-communicating. Further, a third gripping means is connected to the third flow path blocking member, and the third flow path blocking member is held in the direction opposite to the rotational direction of the rotor. When the rotational speed of the rotor is less than a predetermined value, the third flow path blocking member is returned to the position where the liquid chambers are in communication with each other.

In this way, when the liquid chambers are in communication with each other by the third flow path blocking member, the viscous resistance caused by the piston member agitating the viscous fluid due to the movement of the piston member in the liquid chamber is not agitated when the piston member moves. Shear resistance occurs between the viscous fluid and the piston member.

When the rotational speed of the rotor is greater than or equal to the predetermined value, the shear force generated between the rotor becomes larger than the holding force by the third holding means, such that the third flow path blocking member rotates. As a result, the liquid chambers are brought into a non-communication state. Therefore, in addition to the viscous and shear resistance caused by the viscous fluid in the liquid chamber, the compression resistance caused by the compression of the viscous fluid in the liquid chamber by the movement of the piston member is added. Therefore, as the torque acting on the rotor increases, the damping force by the damper increases.

When the rotational speed of the rotor is less than a predetermined value, the shear force generated between the rotor and the rotor is smaller than that of the third fingering means, thereby restoring the third fingering means. As a result, the third flow path blocking member is returned to its original position, whereby the liquid chambers are in communication with each other. Therefore, in the liquid chamber, the compressive resistance by the viscous fluid is reduced and the torque acting on the rotor is lowered, whereby the damping force by the damper is reduced.

According to an aspect of the present invention, there is provided a damper, comprising: a housing, a plurality of liquid chambers formed in the housing, filled with a viscous fluid, and a rotational force transmitted from the outside, and rotatably housed in the housing to form a viscous fluid of the liquid chamber. A rotor that is resisted from the rotor, and has a different shaft center from the rotor, the rotating member to which the rotating force of the rotor is transmitted, a guide protrusion formed by shifting a position from the shaft center of the rotating member, and the guide protrusion A linear guide groove to be fitted is formed, and the oscillating body oscillates in the liquid chamber by the movement of the guide protrusion, and is formed in the oscillating body along the moving direction of the oscillating body, and is substantially divided with the oscillating body interposed therebetween. The pressure reducing passage for bringing the liquid chamber into communication with the oscillator, and the rotational speed of the rotor is greater than or equal to a predetermined value. , By moving by the viscous resistance due to the viscous fluid, including a closure member for closing the pressure flow path characterized in that configured.

In the invention according to claim 8, a plurality of liquid chambers filled with a viscous fluid are formed in the housing. The rotor is rotatably housed in the housing, and the rotor receives resistance from the viscous fluid in the liquid chamber. Further, the housing includes a rotating member having a shaft center different from that of the rotor and to which the rotating force of the rotor is transmitted. The guide protrusion is formed by shifting the position at the shaft center of the rotating member. On the other hand, in the liquid chamber, a rocking member is provided so as to be able to swing, and the rocking body is formed with a linear guide groove engaging with the guide projection. Therefore, the oscillator swings through the guide groove by rotating the guide protrusion by the rotation of the rotating member.

In this way, by converting the rotational movement of the rotor into the oscillation movement of the oscillator, the movement amount of the oscillator can be increased with respect to the movement amount of the rotor. That is, the torque acting on the rotor can be increased.

In addition, a decompression passage is formed in the oscillator along the moving direction of the oscillator, and the liquid chamber almost divided between the oscillators is brought into communication with the decompression passage. Moreover, the oscillator is provided with the blocking member which moves by the viscous resistance by a viscous fluid, when the rotational speed of a rotor becomes more than predetermined value, and a pressure reduction flow path is blocked by the movement of this blocking member.

That is, when the liquid chambers are in communication with each other by the reduced pressure flow path, the viscous resistance caused by the oscillation of the viscous fluid due to the movement of the oscillator in the liquid chamber, and the viscous fluid and the urine that are not stirred when the oscillator moves. Shear resistance occurs between the fuselage and the fuselage.

When the rotational speed of the rotor is greater than or equal to the predetermined value, the viscous fluid of the viscous fluid is increased, so that the blocking member is moved. As a result, the decompression passage is blocked, whereby the liquid chambers which are substantially divided with the oscillator are placed in a non-communication state. Therefore, in addition to the viscous and shear resistance caused by the viscous fluid in the liquid chamber, a compression resistance caused by the compression of the viscous fluid in the liquid chamber by the movement of the oscillator is added. Therefore, as the torque acting on the rotor increases, the damping force by the damper increases.

When the rotational speed of the rotor is less than the predetermined value, the viscous resistance caused by the viscous fluid decreases, so that the blocking member returns to its original position, whereby the decompression flow path is opened, whereby the swinging body is almost sandwiched. The separated liquid chambers are brought into communication. Therefore, in the liquid chamber, the compressive resistance by the viscous fluid is reduced and the torque acting on the rotor is lowered, whereby the damping force by the damper is reduced.

In the damper according to claim 8, the invention according to claim 9 is characterized in that the guide protrusion is engaged with the guide groove so that the oscillator moves in phase with each other.

In the invention as set forth in claim 9, since each oscillator is moved out of phase with each other, each oscillator has a different position in the liquid chamber. Therefore, the torque generated for each liquid chamber can be changed, so that the torque acting on the rotor can be smoothly increased or decreased.

Since the present invention has the above configuration, the torque acting on the rotor can be varied in response to the rotational speed of the rotor.

Hereinafter, the damper which concerns on the 1st Embodiment of this invention is demonstrated.

As shown in FIGS. 1-3, the damper 10 is equipped with the substantially cylindrical housing 12 which has a bottom part. Here, for convenience of explanation, each part will be described with the opening side of the housing 12 as the upper side of the damper 10 and the bottom side as the lower side of the damper 10.

The housing 12 is filled with silicone oil (indicated by dots) as a viscous fluid (to be described later). In addition, the fixing piece 14 is protruded from the outer peripheral surface of the bottom side of the housing 12 at 120 ° intervals, and although not shown, the fixing member of the movable member, which is relatively movable, such as a drawing member that can enter and exit the storage unit. It is possible to fix it. In addition, illustration of the said fixing piece 14 is abbreviate | omitted in 2nd-4th embodiment.

In addition, the inner circumferential surface of the housing 12 is provided with a trocoid gear-shaped portion 16 having a plurality of gear portions 16A (here six), and the trocoid gear-shaped portion (second trocoid gear-shaped portion) 16 ), The height of the upper end surface is lower than the upper end of the housing 12.

And inside the trocoid gear-shaped part 16, the trocoid gear-shaped part (1st trocoid gear) which has the gear part 18A (here, 5) which meshes with the gear part 16A of this trocoid gear-shaped part 16 The hollow inner member (eccentric member) 20 in which the shape part 18 was formed is arrange | positioned, The height of the upper end surface of the gear part 18A of this trocoid gear shape part 18 is the trocoid gear shape part 16. As shown in FIG. It is slightly lower than the upper end surface of 16 A of gear parts.

Moreover, inside the inner member 20, the rotor 22 connected with the transmission member (not shown) which transmits a rotational force can be fitted inside. The rotor 22 is roughly divided into a substantially cylindrical shaft portion 24 and an eccentric portion 26. The rotor 22 has a larger diameter and thinner thickness than the shaft portion 24 between the shaft portion 24 and the eccentric portion 26. A pedestal 28 is formed on the same axis as the shaft 24.

The upper surface of the eccentric portion 26 is almost the same height as the upper surface of the trocoid gear portion 16 in a state where the rotor 22 is inserted inside the inner member 20, and the trocoid gear portion 16 ) And a plate (first flow path blocking member) 30 to be described later can be brought into contact with each other.

Moreover, the eccentric part 26 is provided with the engagement recessed part 36 substantially cylindrical shape on the same axis as the said shaft part 24 of the lower end surface, and protruded in the center part of the bottom surface of the housing 12. It is engaged with the cylindrical engagement convex part 38. As shown in FIG. As a result, the rotor 22 is rotatable at the center of the housing 12.

Further, on the outer circumferential surface of the eccentric portion 26, a plurality of substantially radial ribs 40 protruding from the outer diameter of the shaft portion 24 are formed along the axial direction of the eccentric portion 26. The front end surfaces of the plurality of ribs 40 are located on the same circumference, and the outer circumferential surface of the eccentric portion 26 and the front end surface of the rib 40 abut against the inner circumferential surface of the inner member 20. It is possible.

That is, the inner member 20 is attached to the shaft portion 24 in an eccentric state. When the rotor 22 is rotated, the inner member 20 is pressed by the front end surface of the rib 40, as shown in Figs. 4A and 4B. Rotate eccentrically. At this time, the trocoid gear-shaped portion 18 moves along the shape of the trocoid gear-shaped portion 16 in a state of engaging with the trocoid gear-shaped portion 16 of the housing 12.

On the other hand, as shown in FIG. 3, in the housing 12, the annular cap 42 which becomes substantially L-shaped in cross section can be fitted outside, and the upper end part of the outer peripheral surface of the housing 12 is covered. The shaft portion 24 of the rotor 22 can be inserted into the hole 44 formed in the center portion of the cap 42.

An O-ring mounting groove 32 is formed at the side of the pedestal 28 of the shaft portion 24, and the O-ring 34 is a hole when the O-ring 34 is mounted in the O-ring mounting groove 32. The inner peripheral surface of the portion 44 is in surface contact. As a result, the gap generated between the rotor 22 and the cap 42 is sealed to prevent the silicone oil in the housing 12 from leaking to the outside.

3 and 5, an annular groove 48 is formed on the outer side of the hole 44 on the rear surface of the cap 42. On the outer side of the groove portion 48, a pair of arc-shaped engagement portions 50 are formed concave with the hole portion 44 interposed therebetween.

Moreover, the annular plate 30 can be attached to the back surface of the cap 42. As shown in FIG. 2, an annular rib 52 is formed at an inner circumferential end of the plate 30, and an outer side of the annular rib 52 is formed in an annular rib on a concentric circle of the plate 30. A pair of arc-shaped ribs 54 are formed with 52 in between.

The arc-shaped rib 54 is engaged with the engaging portion 50 in a state in which a gap is formed in the circumferential direction between the engaging portion 50. In addition, as shown in FIG. 3, the annular rib 52 abuts against the inner wall surface of the groove 48 with a gap formed between the groove 48.

The torsion spring (first gripping means) 56 can be attached to a gap formed between the groove 48 and the annular rib 52, and one end of the torsion spring 56 is attached to the plate 30. The other end of the torsion spring 56 is attached to the cap 42.

On the other hand, as shown in FIG. 5, six arc-shaped grooves (first communication paths) 58 are formed on the rear surface side of the plate 30 at predetermined intervals along the concentric circles of the plate 30. This arc-shaped groove 58 is narrower than the thickness of the gear portion 16A of the trocoid gear-shaped portion 16 formed in the housing 12 in plan view as shown in Fig. 6A, In a state where the gear portion 16A and the arc-shaped groove 58 of the trocoid gear-shaped portion 16 overlap each other up and down, both ends of the arc-shaped groove 58 come out of the gear surface of the gear portion 16A. It is in length.

By the way, as shown to (A) and (B) of FIG. 4, in the state which the inner member 20 was arrange | positioned in the housing 12, the trocoid gear-shaped part 16 and the inner member 20 of the housing 12 are carried out. The space (liquid chamber) S is formed between the trocoid gear-shaped part 18 of the (). Silicone oil (indicated by dots) is filled in this space S.

Here, the position of the plate 30 in the circumferential direction is determined by the torsion spring 56 mounted between the groove portion 48 and the annular rib 52. In this state, an arc-shaped rib 54 of the plate 30 is disposed at the center portion of the engaging portion 50 of the cap 42, and as shown in FIG. The position is matched in the position where the groove 58 overlaps with the gear portion 16A of the trocoid gear-shaped portion 16 up and down. In this state, as described above, both ends of the arc-shaped groove 58 are protruded from the gear face of the gear portion 16A.

That is, as shown in (A) and (B) of FIG. 4, the space S formed by the trocoid gear-shaped portion 16 and the trocoid gear-shaped portion 18 of the inner member 20 has a trocoid gear shape. As shown in FIGS. 3 and 6, the adjacent spaces Sl partitioned by the respective gear portions 18A of the portion 18 communicate with each other by the arc-shaped grooves 58 of the plate 30. The state {hereinafter, simply referred to as a communication state}. Therefore, the silicone oil can flow to the spaces Sl through the arc-shaped grooves 58.

On the other hand, the arc-shaped rib 54 of the plate 30 is capped by the stress 42 in the direction of resisting the holding force of the torsion spring 56 (stress for rotating the plate 30 forward or reverse). When it comes in contact with the end face of the engaging portion 50 of Fig. 6B, as shown in Fig. 6B, one end side of the arcuate groove 58 is closed by the trocoid gear-shaped portion 16 when viewed in plan view. As shown in FIGS. 4A and 4B, the spaces Sl partitioned by the respective gear portions 18A of the trocoid gear-shaped portion 18 are in a non-communication state.

Subsequently, the operation of the damper according to the first embodiment of the present invention will be described.

When the rotor 22 is rotated at a low speed, as shown in FIGS. 4A and 4B, the inner member 20 passes along the shape of the trocoid gear 16 through the eccentric portion 26. Rotate As a result, the silicone oil in the space S is agitated by the gear portion 18A of the inner member 20, so that the viscosity resistance of the silicone oil is generated in the space S. As shown in FIG.

In addition, at this time, when the gear part 18A of the inner member 20 moves in the trocoid gear-shaped part 16, shear resistance generate | occur | produces between silicone oil which is not stirred and the gear part 18A.

Further, the space Sl formed by the gear portion 16A of the trocoid gear-shaped portion 16 and the gear portion 18A of the trocoid gear-shaped portion 18 of the inner member 20 is the gear portion 18A. By gradually narrowing with the movement of, the silicone oil is compressed, and thus compression resistance by the silicone oil occurs in the space Sl.

That is, as the inner member 20 rotates, the torque generated by the viscous resistance, shear resistance, and compression resistance caused by silicone oil acts on the rotor 22, and this torque is the rotational speed of the rotor 22. It becomes large in proportion to (torque 1 shown in FIG. 7).

As shown in FIG. 6A, each space Sl in the housing 12 is in communication with the spaces Sl adjacent to each other by the arc-shaped groove 58 of the plate 30. The silicone oil is in a state in which the silicon S can flow in the spaces S1 adjacent to each other via the arc-shaped groove 58.

Therefore, compared with the case where the spaces Sl adjacent to each other become in non-communication state, the said compression resistance is reduced, and the damping force by the damper 10 is reduced by the torque acting on the rotor 22 by that much. This will be reduced.

3, the plate 30 which contacts the upper surface of the eccentric part 26 of the rotor 22 is between the upper surface of the eccentric part 26 by rotation of the rotor 22. As shown in FIG. The shear force or the flow force of the viscous fluid is generated, but the rotation of the plate 30 is restricted by the holding force of the torsion spring 56 mounted on the plate 30.

However, when the rotor 22 is rotated at a high speed, the shear force or the flow force of the viscous fluid generated between the plate 30 and the upper surface of the eccentric portion 26 becomes large, and is caused by the torsion spring 56. It will exceed the force. In this manner, when the shear force becomes larger than the holding force by the torsion spring 56, the plate 30 rotates.

And in the state which the arc-shaped rib 54 (refer FIG. 2) of the plate 30 abuts on the cross section of the engaging part 50 (refer FIG. 5) of the cap 42, shown to FIG. 6 (B). As seen from the plane, one end side of the arc-shaped groove 58 of the plate 30 is closed by the trocoid gear-shaped portion 16 so that the spaces S1 adjacent to each other become in non-communication state. As a result, the compressive resistance of the silicone oil in the space Sl is increased, so that the torque acting on the rotor 22 is increased, thereby increasing the damping force by the damper 10 (in FIG. 7). Indicating torque 2).

In this state, since the torsion spring 56 is held in the direction that resists the holding force, the torsion spring 56 is in a state where elastic energy (restoration force) is accumulated. Therefore, when the rotational speed of the rotor 22 is slowed and the shear force or the flow force of the viscous fluid generated between the plate 30 and the upper surface of the eccentric portion 26 becomes smaller than the elastic energy, the torsion spring By restoring 56 and returning the plate 30 to its original position, as shown in Fig. 6A, spaces S1 adjacent to each other are in communication with each other. As a result, the torque acting on the rotor 22 returns to its original state (state of torque 1).

That is, according to this embodiment, as shown in FIG. 7, the torque acting on the rotor 22 can be varied (torque 1 and torque 2) in accordance with the rotational speed of the rotor 22. Moreover, by adjusting the holding force of the torsion spring 56, as shown in FIG. 8, the rotational speed of the rotor 22 and the switching position P of the low torque (torque 1) and high torque (torque 2) are adjusted. You can easily change it.

In addition, in this embodiment, as shown in FIG. 5, six circular arc grooves 58 are formed in the back surface side of the plate 30, and the substantially circular rib-shaped ribs (58) are formed between adjacent arc-shaped grooves 58 which are adjacent to each other. 60, but both ends of the arc-shaped groove 58 are overlapped with the gear portion 16A and the arc-shaped groove 58 of the trocoid gear portion 16 formed in the housing 12. The length of the rib 60 is not limited to this, as long as it has a length protruding from the gear portion 16A. For example, as shown in FIG. 9, the rib 60 for partitioning the arc-shaped groove 58 may be a triangular rib 62 forming a triangle when viewed in a plan view.

Next, the damper which concerns on 2nd Embodiment of this invention is demonstrated.

As shown in FIGS. 10-12, the damper 100 is equipped with the substantially cylindrical housing 102 which has a bottom part. Here, for convenience of explanation, each part will be described with the opening side of the housing 102 as the upper side of the damper 100 and the bottom side as the lower side of the damper 100.

The housing 102 is filled with silicone oil, and the rod-shaped rotor 104 is accommodated in the housing 102. One end side of the rotor 104 is smaller in diameter than the other end side, and is connected to a transmission member (not shown) which is exposed to the outside and transmits rotational force.

On the other end side of the rotor 104, a cam groove (cam means) 106 having a corrugation having a ridge and a curve is formed along the axial direction of the rotor 104, and the number of corrugations is formed. Has four. On the other end side of the rotor 104, a substantially cylindrical collar 108 is fitted from the outside.

A small diameter portion 109 is formed on the upper end side of the collar 108, and a step 109A is formed on the inner peripheral surface side of the collar 108 by the small diameter portion 109. In addition, an O-ring mounting groove 110 is formed at an edge of the step 109A, and an O-ring 112 is mounted in the O-ring mounting groove 110. The O-ring 112 prevents silicone oil from leaking out between the collar 108 and the rotor 104.

In addition, three rectangular holes 114 are formed in the collar 108 at positions corresponding to the cam grooves 106 at intervals of 120 °, and the collar 108 covers the rectangular holes 114 on the outer side of the collar 108. Plate-shaped chips (moving members) 116 formed in an arc shape in accordance with the outer circumferential surface of 108 are formed, respectively.

An engaging protrusion (cam means) 118 is formed at the inner central portion of the chip 116, and the engaging protrusion 118 of the rotor 104 is formed through the rectangular hole 114 of the collar 108. It is possible to engage the cam groove 106. Accordingly, the chip 116 reciprocates along the axial direction of the rotor 104 through the cam groove 106 and the engaging protrusion 118 by the rotation of the rotor 104 (see FIG. 13). At this time, the respective chips 116 move with different phases.

A gap is formed between the chips 116 adjacent to each other, and an orifice 120 is formed on the side surface of the chip 116 along the moving direction of the chips 116.

Here, in order to avoid interference with the chip 116 attached to the collar 108, an approximately rectangular chip accommodating portion 122 having an upper opening is formed in the inner circumferential surface of the housing 102 to be concave. Then, the silicon oil is filled in the chip housing 122, and the chip 116 reciprocates along the axial direction of the rotor 104 in the chip housing 122.

In addition, as shown in FIG. 12, in the state where the engaging protrusion 118 of the chip 116 is disposed at the center of the peak and curved portions of the cam groove 106, the upper portion of the chip receiving portion 122 will be described later. The gap {space S1} formed between the lower surface of the jaw portion 126 of the inner cap 124 and the upper surface of the chip 116, the bottom surface of the chip receiving portion 122, and the lower surface of the chip 116. The clearance gap (space S2) formed between the surfaces is the same size. That is, there is no difference according to the moving direction of the chip 116 with respect to the compressive force of the silicone oil generated when the chip 116 reciprocates.

On the other hand, as shown in Figs. 14 and 16 (A), between the rectangular hole 114 and the rectangular hole 114 formed in the central portion of the collar 108, both sides along the axial direction of the collar 108 are located. A rectangular communication recess 128 is formed, and a gap is formed between the chip 116.

At the upper end of the collar 108, a cam surface 108A formed in an inverted triangle is formed. An annular cam 132 fitted to the outside of the rotor 104 is disposed above the collar 108, and a cam surface 132A capable of surface contact with the cam surface 108A is formed at the lower end of the cam 132. It is to be fitted with each other.

In addition, an inner cap 124 having a substantially cylindrical shape is fitted to the outside of the cam 132 from the outside. A positioning groove 134 is formed in the inner circumferential surface of the inner cap 124, and the positioning groove 134 has a positioning rib protruding along the axial direction of the cam 132 on the outer circumferential surface of the cam 132. 136 is made to be able to engage. The cam 132 is prevented from rotating relative to the inner cap 124 while the positioning rib 136 is engaged with the positioning groove 134.

On the other hand, a gap is formed at an upper portion of the cam 132 with an annular portion 124A formed inside the upper end of the inner cap 124, and a coil spring (second support member) 137 is formed in the gap. It is arrange | positioned, The one end part contacts the annular part 124A, and the other end touches the cam 132, and the said cam 132 is supported by the collar 108 side. As a result, the cam surface 108A of the collar 108 is engaged with the cam surface 132A of the cam 132 (the state where the curved portion of the cam surface 108A and the peak of the cam surface 132A coincide). maintain.

By the way, the step part 138 is formed in the outer peripheral surface of the collar 108 by the small diameter part 109 formed in the upper end part side. On the other hand, an annular pedestal 140 is formed inside the upper end of the housing 102, and has a height substantially equal to the stepped portion 138 in the state where the collar 108 is accommodated in the housing 102. It is.

The lower end of the inner cap 124 fitted to the outer side of the collar 108 is provided with a jaw portion 126, and the lower surface of the jaw portion 126 abuts against the step portion 138 and the pedestal portion 140. . Then, the lower surface of the jaw portion 126 is fixed to the pedestal portion 140. This prevents the cam 132 from rotating through the inner cap 124 and the inner cap 124.

In this state, the upper surface of the upper portion of the jaw portion 126 of the inner cap 124 and the upper end of the housing 102 are in a coincidence state, and are formed to cover the upper portion of the jaw portion 126 of the inner cap 124. The outer cap 142 having the 142A formed thereon is screwed to the threaded portion 102A formed on the outer circumferential surface of the housing 102, so that the inner cap 124 is fixed to the housing 102 through the outer cap 142. do.

Here, O-ring attachment portions 144 and 146 are formed at the outer and inner circumferences of the lower surface of the jaw portion 126, and the O-rings 148 and 150 are mountable, respectively. The o-ring 148 prevents silicone oil from leaking out between the inner cap 124 and the housing 102, and the o-ring 150 is disposed between the inner cap 124 and the collar 108. To prevent silicone oil from leaking outside.

However, the cam surface 132A of the cam 132 is shown by the holding force of the coil spring 137 disposed between the upper portion of the cam 132 and the annular portion 124A of the inner cap 124. In a state where the cam surface 108A of the collar 108 is engaged with the cam 108, the communication recess 128 formed in the collar 108 is formed in the housing 102 in a state where the collar 108 is accommodated in the housing 102. Facing ribs (pillars) 130 which partition the adjacent chip receiving portions 122 formed therebetween face each other, and are protruded to both sides of the partition ribs 130.

That is, as shown in FIG. 16A, a gap is hardly formed between the outer circumferential surface of the collar 108 and the partition rib 130, but there is a gap between the communication recess 128 and the partition rib 130. Is formed and the communication recess 128 is protruded from both sides of the partition rib 130, so that the chip receiving portions 122 adjacent to each other through the communication recess 128 are in communication with each other. The spaces S1 and the spaces S2 adjacent to each other are brought into communication.

On the other hand, as shown in FIG. 15, the cam surface 132A of the cam 132 by the stress in the direction which resists the holding force of the coil spring 137 (stress which makes the color 108 turn forward or reverse rotation). ) And the cam surface 108A of the collar 108 are released, the end of the communication recess 128 is closed by the partition rib 130 as shown in Fig. 16B. Will be. That is, the chip receiving portions 122 adjacent to each other are in non-communication state (the spaces S1 and the spaces S2 adjacent to each other are in non-communication state).

Subsequently, the operation of the damper according to the second embodiment of the present invention will be described.

When the rotor 104 is rotated at a low speed, as shown in FIG. 13, the chip 116 is moved through the cam groove 106 formed in the rotor 104 and the engaging protrusion 118 formed in the chip 116. In accordance with the shape of the cam groove 106, the chip receiver 122 reciprocates along the axial direction of the rotor 104.

Thereby, in the chip accommodating part 122 shown to FIG. 14 and FIG. 16A, the viscous resistance and the chip 116 which arise when the chip 116 stirs the silicone oil in the chip accommodating part 122 are shown. During this movement, shear resistance occurs between the inner wall of the chip housing 122.

Here, for example, when the chip 116 moves upward, the gap {space S1} formed between the upper surface of the chip 116 and the lower surface of the jaw portion 126 of the inner cap 124 becomes narrow. As a result, compression resistance caused by silicone oil is generated.

However, since each chip 116 moves out of phase with each other, all three chips 116 do not move in the same direction. Therefore, as shown in FIG. 14, in the state where the space S1 comprised by the movement of the chip 116 becomes narrow, the space S1 comprised by the adjacent chip 116 becomes large.

On the other hand, since the communication recess 128 formed in the collar 108 is almost faced with a gap formed between the partition ribs 130 and protrudes from both sides of the partition ribs 130, the communication recesses 128 are formed. The chip housing portions 122 adjacent to each other communicate with each other through the recess 128 (the spaces S1 and the spaces S2 adjacent to each other communicate with each other).

Therefore, when the space is narrowed by the movement of the chip 116, the silicone oil in this space moves to the adjacent chip receiving portion 122 through the communication recess 128 of the collar 108, and thus, the silicone oil. The compression resistance by is small.

That is, as the chip 116 reciprocates, the rotor 104 mainly acts on the viscous resistance due to the silicone oil and the torque due to the shear resistance. As the compression resistance is reduced, the torque acting on the rotor 104 is reduced by that, and the damping force by the damper 100 is reduced.

By the way, as shown in FIG. 12, although the shear force is generated in the collar 108 which contacts the rotor 104, with the rotor 104 by the rotation of the rotor 104, the coil spring 137 The rotation of the collar 108 is regulated by engaging the cam surface 132A of the cam 132 with the cam surface 108A of the collar 108 by means of the holding force.

However, when the rotor 104 is rotated at a high speed, the shear force generated between the rotor 104 and the collar 108 becomes large, and exceeds the holding force by the coil spring 137. As described above, when the shear force becomes larger than the holding force by the coil spring 137, the collar 108 rotates as shown in FIG. 15, whereby the cam surface 108A and the cam 132 of the collar 108 are rotated. Position shift | offset | difference occurs with cam surface 132A.

The position of the communication recess 128 is shifted as shown in FIGS. 15 and 16B by the rotation of the collar 108, so that one end side of the communication recess 128 is divided into ribs ( 130) to occlude. That is, the chip receiving portions 122 adjacent to each other are in a non-communication state (the spaces S1 and the spaces S2 adjacent to each other are in non-communication state).

As a result, the silicon oil in the space narrowed by the movement of the chip 116 is compressed, and the flow path of the silicon oil due to the movement of the chip 116 is limited to the orifice 120 formed on the side of the chip 116. Will be.

That is, the rotor 104 is provided with a compressive resistance by the silicone oil in addition to the viscosity resistance and shear resistance caused by the silicone oil, thereby increasing the torque acting on the rotor 104, and thus the damper 100 The damping force becomes large.

Here, due to the rotation of the collar 108, the coil spring 137 has an axial force along the axial direction of the cam 132 via the cam surface 108A of the collar 108 and the cam surface 132A of the cam 132. Since the force is applied, elastic energy (restoration force) is stored.

Therefore, when the rotational speed of the rotor 104 is slowed and the shear force generated between the rotor 104 and the collar 108 becomes smaller than the elastic energy, the coil spring 137 is restored and at the same time the cam By returning the collar 108 to its original position via the 132, the chip receiving portions 122 adjacent to each other are brought into communication as shown in Figs. 14 and 16A (the spaces adjacent to each other). (S1) and the space (S2) are in communication with each other}. As a result, the torque acting on the rotor 104 returns to its original state.

That is, according to this embodiment, the torque acting on this rotor 104 can be changed according to the rotational speed of the rotor 104. In addition, by adjusting the holding force of the coil spring 137, it is possible to easily change the rotational speed of the rotor 104 and the switching positions of low torque and high torque.

Further, on the outer circumferential surface of the rotor 104, a cam groove 106 having a waveform having a peak and a curved portion is formed along the axial direction of the rotor 104, and the cam groove 106 is rotated by the rotor 104. By moving the chip 116 to be reciprocated along the axial direction of the rotor 104, the movement amount of the chip 116 can be increased with respect to the movement amount of the rotor 104. That is, the viscosity resistance and the shear resistance of the silicone oil can be increased.

In addition, since each chip 116 is moved out of phase with each other, each chip 116 has a different position in the chip receiving portion 122. Accordingly, the torque generated for each chip receiving portion 122 can be converted, so that the torque acting on the rotor 104 can be smoothly increased or decreased.

In addition, in this embodiment, although the chip 116 was made into circular arc shape in plan view in consideration of the compression efficiency of silicone oil, since the chip 116 is formed corresponding to the chip accommodating part 122, it must necessarily be circular arc shape. There is no.

In addition, the number of waveforms of the cam groove 106 is set to four, the chip 116 is set to reciprocate four times when the rotor 104 rotates once, and the chips 116 are set to three. ) Do not all operate in the same direction, but the pulsation or torque of the chip 116 is adjusted by changing the shape of the cam groove 106 (cycle period, number of waveforms, etc.) or the number of chips 116. You may also do it.

In addition, a sealing function may be formed in the collar 108 so that silicone oil does not flow into the cam groove 106 of the rotor 104. In addition, although the torque was switched by rotating the collar 108 to shift the position of the communication recess 128, a valve (not shown) is formed in the adjacent spaces S1 and S2 to control the flow of the silicone oil. You may also

Next, the damper which concerns on 3rd Embodiment of this invention is demonstrated.

As shown in FIGS. 17-19, the damper 200 is equipped with the substantially cylindrical housing 202 which has a bottom part. Here, for convenience of explanation, each component will be described with the opening side of the housing 202 as the upper side of the damper 200 and the bottom side as the lower side of the damper 200.

The housing 202 is filled with silicone oil, and the guide ribs 204 are formed at three locations on the inner circumferential surface of the housing 202 at 120 ° intervals along the circumferential direction of the housing 202. In addition, a substantially cylindrical mounting recess 206 is formed in the center of the bottom of the housing 202.

On the other hand, the attachment convex part 210 protrudes in the center part of the lower surface of the substantially disk-shaped valve (3rd flow path blocking member) 208, and it can be engaged with the said attachment recessed part 206. As shown in FIG. The valve 208 is rotatable relative to the housing 202 in a state where the attachment convex portion 210 is engaged with the attachment concave portion 206.

In addition, on the outer circumferential surface of the valve 208, there are three vortex pieces 212 extending in the counterclockwise direction (the reverse direction of the rotation direction of the rotor 244 described later) at intervals of 120 ° along the circumferential direction of the valve 208. It is formed in.

One end of the tension spring (third finger member) 214 is attached to the distal end of the vortex piece 212, the other end of the tension spring 214 is mounted to the housing 202, and the vortex piece 212 is provided. The valve 208 is held in the direction that rotates counterclockwise through.

Moreover, the substantially cylindrical flow path body 216 is formed in the center part of the upper surface of the valve 208. As shown in FIG. In this flow path body 216, three flow paths (third communication paths) 218 which are spaced apart from each other at 120 ° intervals are formed concave. Moreover, the upper surface of the flow path body 216 is a concave curved surface, and the upper surface of this flow path body 216 is formed in the pentagon shape (or circumferential shape) which consists of the small sphere 220 and the large sphere 222. Piston body (swinging member) 224 can be placed.

On the other hand, in the housing 202, an inner housing 225 having an arc shape when viewed in plan view can be accommodated, and a guide groove 226 is formed in the rear center portion of the inner housing 225 along the height direction thereof. It is. The guide groove 226 is able to engage with the guide rib 204 of the housing 202, the inner housing 225 is rotated while the guide rib 204 is engaged with the guide groove 226. Is prevented.

Moreover, the large sphere 222 of the piston body 224 is accommodated inside the inner housing 225, and the large sphere 222 of the piston body 224 is accommodated inside the inner housing 225. In the state, the small sphere 220 of the piston body 224 is exposed on the upper surface of the inner housing 225.

Moreover, in order to accommodate the large sphere 222 of the piston body 224 inside the inner housing 225, the upper end of the inner housing 225 conforms to the spherical shape of the large sphere 222 of the piston body 224, and It has the concave curved surface 228 formed except the lower end part. An approximately rectangular piston accommodating portion 230 is formed in the center of the curved surface 228, and passes through the curved surface 228 in the center of the lower edge portion of the piston accommodating portion 230 to the lower end of the inner housing 225. A facing orifice 232 is formed.

In addition, silicone oil is filled in the piston accommodating part 230, and silicone oil in the piston accommodating part 230 is allowed to flow in the orifice 232. The orifice 232 is capable of communicating with the flow path 218 formed in the flow path body 216 of the valve 208, and the positions of the orifice 232 and the flow path 218 as shown in Fig. 21A. Is matched, the silicone oil in the piston receiving portion 230 is allowed to flow into the flow path 218 through the orifice 232. That is, the piston accommodating parts 230 adjacent to each other through the flow path 218 are in communication with each other.

By the way, as shown in FIGS. 17-19, on the outer peripheral surface of the large sphere 222 of the piston body 224, the substantially rectangular curved recessed part 234 is 120 degrees so that it may conform to the spherical shape of this large sphere 222. As shown to FIG. It is formed in three places at intervals. An approximately cylindrical fitting recess 236 is formed at the center of the curved recess 234, and the fitting protrusion formed on the inner surface side of the engaging piece 238 engaged with the curved recess 234. 240 can be fitted.

The outer surface of the engagement piece 238 coincides with the outer surface of the large sphere 222 of the piston body 224 in a state where the fitting projection 240 is fitted to the fitting recess 236. In addition, a piston (piston member) 242 protrudes from the center of the outer surface of the engaging piece 238. The piston 242 is to be received in the piston receiving portion 230.

By the way, the upper side of the outer peripheral surface of the inner housing 225 is a small diameter part, and the clearance gap is formed between the inner peripheral surface of the housing 202. As shown in FIG. In this gap, an annular guide piece 246 draped downward from the bottom outer periphery of the large diameter portion side of the substantially cylindrical rotor 244 composed of two stages is insertable.

The transmission member (not shown) which transmits a rotational force is connectable to the small diameter part side of the rotor 244, and the bottom part of the large diameter part side of the rotor 244 abuts on the upper surface of the inner housing 225, The rotor 244 rotates along the circumferential direction of the housing 202 through the guide piece 246.

In addition, an annular cap 248 can be fitted on the small diameter side of the rotor 244, and the cap 248 is fixed to the housing 202. As a result, the rotor 244 is prevented from being pulled out of the housing 202. Here, the O-ring mounting portion 250 is formed at the lower edge portion of the inner circumferential surface of the cap 248, and the O-ring 252 is mounted on the O-ring mounting portion 250. This prevents the silicone oil filled in the housing 202 from leaking outside.

In addition, at the bottom portion of the large diameter portion side of the rotor 244, a connection portion 254 is formed to connect the small sphere 220 of the piston body 224 to a position displaced from the axial center of the rotor 244. When the small sphere 220 of the piston body 224 is connected by the connecting portion 254, the piston body 224 is placed on the valve 208 in an inclined state.

When the rotor 244 is rotated, the piston body 224 swings around the point P through the small sphere 220. At this time, as shown in Figure 22, the piston 242 of the piston body 224 is moved up and down while oscillating in the piston receiving portion 230, each piston 242 is moved in phase with each other.

By the way, the position of the valve 208 is determined by the holding force of the tension spring 214 attached to the vortex piece 212, as shown in Fig. 21A, the flow path formed in the flow path body 216 218 is in a position to communicate with the orifice 232 of the piston receiving portion 230. Therefore, the silicone oil in the piston accommodating part 230 flows to the flow path 218 through the orifice 232, and the piston accommodating parts 230 which are adjacent to each other through this flow path 218 are in communication.

On the other hand, when the valve 208 rotates as shown in FIG. 21B by the stress in the direction which resists the holding force of the tension spring 214, the position of the flow path 218 of the flow path body 216 By shifting, the end of the orifice 232 of the piston accommodating portion 230 is closed by the circumferential wall of the flow path body 216. That is, the piston accommodating parts 230 adjacent to each other by the flow path 218 are in a non-communication state.

Next, the action of the damper according to the third embodiment of the present invention will be described.

When the rotor 244 is rotated at a low speed, as shown in FIG. 22, the piston body 224 oscillates around the point P with the rotation of the rotor 244, whereby the piston body 224 is rotated. The piston 242 formed in the to move up and down while swinging in the piston receiving portion (230).

Thereby, in the piston accommodating part 230, the viscous resistance which arises by stirring the silicone oil in the piston accommodating part 230, and the inner wall of the piston accommodating part 230 when the piston 242 moves. Shear resistance occurs between and.

Here, as shown in FIG. 19, when the piston 242 moves upward, the gap formed between the upper end surface of the piston 242 and the piston accommodating portion 230 is narrowed, so that the compression resistance by the silicone oil is reduced. Although the three pistons 242 move out of phase with each other, the position in the piston accommodating part 230 is different.

That is, in the state where the clearance gap formed between the upper end surface of the piston 242 and the piston accommodating part 230 became narrow, the clearance gap comprised between the upper end surface of the adjacent piston 242 and the piston accommodating part 230 becomes large. I am supposed to lose.

Therefore, when the piston 242 moves downward, the silicone oil in the piston accommodating portion 230 adjoins via the flow path 218 of the valve 208 via the orifice 232 formed in the piston accommodating portion 230. Since it moves to the piston accommodating part 230, the compression resistance by silicone oil is small.

That is, as the piston 242 reciprocates, the rotor 244 mainly acts on viscous resistance due to silicone oil and torque due to shear resistance. As the compression resistance is reduced, the torque acting on the rotor 244 is reduced by that, and the damping force by the damper 200 is reduced.

However, the shear force is generated in the valve 208 in contact with the piston body 224 between the piston body 224 due to the swing of the piston body 224, but the valve 208 is a shot of the tension spring 214. Position is determined by intellect.

However, when the rotor 244 is rotated at a high speed, the shear force generated between the piston body 224 and the valve 208 becomes large, and exceeds the holding force by the tension spring 214. As described above, when the shear force becomes larger than the holding force by the tension spring 214, the valve 208 rotates as shown in Fig. 20B.

By this rotation, as shown in FIG. 21B, the position of the flow path 218 of the valve 208 is shifted from the position of the orifice 232 of the piston accommodating portion 230. As a result, the end portions of the orifice 232 of the piston accommodating portion 230 are closed by the circumferential wall of the flow path body 216, so that the piston accommodating portions 230 adjacent to each other are in a non-communication state.

Therefore, the silicone oil in the space narrowed by the movement of the piston 242 is compressed, so that the compressive resistance by the silicone oil becomes larger than when the rotor 244 is rotated at low speed. The torque acting on the electrons 244 is increased. That is, the damping force by the damper 200 is increased.

Here, since the elastic force (restoration force) is accumulated in the tension spring 214 by moving the valve 208 in the direction that resists the holding force of the tension spring 214, the rotor 244 When the rotational speed is slowed and the shear force generated between the piston body 224 and the valve 208 becomes smaller than the elastic energy, as shown in Figs. 20A and 21A, As the tension spring 214 is restored and the valve 208 is returned to its original position, the torque acting on the rotor 244 is returned to its original state.

That is, according to this embodiment, the torque acting on this rotor 244 can be changed according to the rotational speed of the rotor 244. Moreover, by adjusting the holding force of the tension spring 214, the rotational speed of the rotor 244 and the switching position of low torque and high torque can be changed easily.

In addition, by converting the rotational force of the rotor 244 to the oscillation force of the piston body 224 to cause the piston 242 formed on the outer peripheral surface of the piston body 224 to move up and down, the movement amount of the rotor 244 The amount of movement of the piston 242 may be increased.

Further, since the pistons 242 are moved out of phase with each other, the pistons 242 have different positions in the piston accommodating portion 230. Accordingly, the torque generated in each piston accommodating portion 230 can be changed, so that the torque acting on the rotor 244 can be smoothly increased or decreased.

In addition, in this embodiment, as shown in FIG. 18, the engaging recess 234 is formed in the large sphere 222 of the piston body 224, and is engaged with the curved recessed portion 234. 238 is formed and the piston 242 is formed on the engagement piece 238. However, as shown in FIG. 23, the large sphere 222 and the piston 242 of the piston body 224 are integrally formed. You may form.

In this embodiment, as shown in FIGS. 20A and 20B, the vortex piece 212 extends from the outer circumferential surface of the valve 208, and a tension spring ( 214 is attached and the valve 208 is held in the counterclockwise direction by the tension spring 214, but this is a configuration in which the rotation direction of the rotor 244 is one direction.

Therefore, when the rotor 244 rotates forward and reverse, as shown in FIG. 24A, the inner side of the vortex piece 212 forms an obtuse angle with the vortex piece 212. The bent portion 212A, which was bent and folded, was formed successively, and an approximately triangular inclined portion 202A was concavely formed on the inner circumferential surface of the housing 202, and the vortex piece 212 was formed along the shape of the inclined portion 202A. It will bend inward to move.

That is, when the valve 208 rotates clockwise by the shear force generated between the piston body 224 by the forward rotation of the rotor 244, the vortex piece 212 is inclined as shown by the imaginary line. It moves along the part 202A, whereby the elastic energy (restoration force) is accumulated by the elastic piece 212 elastically deforming. Therefore, in this case, the tension spring 214 becomes unnecessary.

When the rotation speed of the rotor 244 is slowed down and the shear force generated between the piston body 224 and the valve 208 becomes smaller than the above-mentioned elastic energy, as shown by the solid line, the vortex piece ( As soon as 212 is restored, the valve 208 returns to its original position (the position indicated by the solid line), so that the torque acting on the rotor 244 returns to its original state.

On the other hand, when the rotor 244 is rotated in reverse, as shown in FIG. 24B, the vortex piece 212 moves counterclockwise along the shape of the inclined portion 202A. In this case, elastic energy (restoration force) is accumulated by the elastic piece 212 being elastically deformed.

In addition to the configuration shown in Figs. 24A and 24B, although not shown, a torsion spring is disposed between the housing and the valve, and the torsion spring determines the position in the circumferential direction of the valve. Then, the valve can be rotated forward and reverse by the shear force generated between the piston body by the rotation of the rotor. In this case, since the elastic energy is accumulated in the torsion spring, the vortex piece 212 becomes unnecessary.

Next, the damper which concerns on 4th Embodiment of this invention is demonstrated.

The damper 300 shown to FIGS. 25-26 is equipped with the substantially cylindrical housing 302 which has a bottom part. Here, for convenience of explanation, each component will be described with the opening side of the housing 302 as the upper side of the damper 300 and the bottom side as the lower side of the damper 300.

A shaft hole 308 is formed in the center of the bottom of the housing 302 to axially support the rod-shaped rotor 304 connected to a transmission member (not shown) that transmits rotational force. Further, a fan-shaped accommodating part (liquid chamber) 310 is formed in the bottom of the housing 302 at intervals of 120 degrees, and the accommodating part 310 is filled with a silicone oil, and is substantially flat. The oscillating body 312 is accommodated so as to oscillate.

In addition, at the bottom of the receiving portion 310, a shaft hole 315 is formed in engagement with the shaft portion 314 formed on the lower surface of the swinging body 312, and the shaft portion 314 is formed in the shaft hole 315. In the engaged state, the swinging body 312 can swing around the shaft portion 314.

The upper surface of the oscillator 312 is formed with the shaft portion 316 on the same axis as the shaft portion 314, the guide groove 320 along the radial direction of the oscillator 312 in the center of the upper surface of the oscillator 312 ) Is formed.

In the housing 302, a substantially disk-shaped guide plate 330 is fixed to the bottom of the housing 302, and a through hole 332 through which the rotor 304 penetrates is formed at the center of the guide plate 330. Formed. The rotor 304 has an O-ring mounting groove 350 formed at a position corresponding to the through hole 332, and the O-ring 352 is mounted in the O-ring mounting groove 350. By contacting the inner circumferential surface of the through hole 332, the 352 prevents the silicon oil from leaking to the surface of the guide plate 330 through the through hole 332.

In addition, the guide plate 330 is formed with a shaft hole 335 which is engaged with the shaft portion 316 formed in the through hole 334 and the oscillator 312 at intervals of 120 °, and corresponds to the housing portion 310. It is supposed to. An approximately fan-shaped depression 336 is formed between the through-holes 334 adjacent to each other, and this portion has a thin thickness.

In the through hole 334, a gear member (rotating member) 338 can be mounted, respectively. The gear member 338 is provided with a gear 340 in the upper portion, and a substantially cylindrical sealing portion 342 is formed in the lower portion of the gear 340.

The O-ring mounting groove 344 is formed on the outer circumferential surface of the sealing portion 342, and the O-ring 346 is a through hole in the state where the O-ring 346 is mounted in the O-ring mounting groove 344. Contact with the inner circumferential surface of 334 prevents the silicone oil from leaking to the surface of the guide plate 330 through the through hole 334.

And the rod-shaped guide boss (guide protrusion) 348 protrudes from the back surface of the sealing part 342 at the position shifted from the axial center of the gear 340. As shown in FIG. Accordingly, when the gear 340 rotates, the guide boss 348 rotates about the axis center of the gear 340.

The guide boss 348 can be engaged with the guide groove 320 formed on the upper surface of the swinging body 312. Therefore, as shown in FIGS. 28A to 28D, the movement of the guide boss 348 due to the rotation of the gear 340 (that is, rotation about the axis center of the gear 340) is achieved. The oscillator 312 is moved through the guide groove 320 engaged with the guide boss 348. The guide boss 348 rotates about the axis of the gear 340 with respect to the guide groove (3). Since the 320 is linear, the swinging body 312 swings around the shafts 314 and 316 in the receiving portion 310 through the guide groove 320.

At this time, since the position of the guide boss 348 with respect to the gear 340 is different for each guide boss 348, the position of the guide boss 348 in the guide groove 320 of each oscillator 312 is all Different. Here, a large gear 354 is fitted to the rotor 304 and is rotatable integrally with the rotor 304. Since the large gear 354 is meshed with each gear 340, rotating the rotor 304 causes each gear 340 to rotate through the large gear 354.

By the way, the housing 302 is attached with the substantially annular cover body 356 which a rotor 304 can penetrate. The lower surface of the lid 356 is provided with a positioning concave portion 360 engaged with the positioning convex portion 358 formed on the upper surface of the gear 340. An arc-shaped opening 362 is formed at a position corresponding to the depression 336 of the guide plate 330 of the lid 356. In addition, abutment ribs 364 protrude from the inner edge portion of the lower surface of the lid 356, and abut against the upper surface of the large gear 354. This prevents the rotor 304 from being pulled out of the housing 302.

By the way, as shown in FIG. 29, the accommodating recessed part 324 in which the valve | bulb (close member) 321 of a substantially ginkgo leaf shape is accommodated in the lower surface of the oscillation body 312 is formed. The accommodation recess 324 is formed slightly larger than the shape of the valve 321, and the valve 321 is allowed to swing along the swinging direction of the swinging body 312 within the accommodation recess 324. {See FIG. 30 (B), (D)}.

As shown in FIGS. 30A to 30D (FIG. 30A is a cross-sectional view taken along the line AA of (B), and FIG. 30C is a cross-sectional view taken along the line BB of (D)). The portion 324 is formed with a gap between the front end of the straight plate portion 326 constituting the valve 321, and in the region where the plate portion 326 is accommodated along the swinging direction of the swinging body 312. The flow path 328 through which the silicone oil can pass is formed. As a result, the accommodating portion 310 which is almost divided by the swinging body 312 is brought into communication.

On the other hand, the valve 321 in the accommodation concave portion 324 swings due to the viscous resistance of the silicone oil passing through the flow path 328 due to the swinging of the swinging body 312. When one side of the flow path 328 is blocked by the plate portion 326, the receiving portion 310 almost divided by the oscillator 312 is in a non-communication state.

Next, the action of the damper according to the fourth embodiment of the present invention will be described.

Rotating the rotor 304 at low speed causes each gear 340 to rotate through the large gear 354 as shown in FIG. By rotation of this gear 340, the guide boss 348 formed in each gear member 338 rotates about the axial center of the gear 340, as shown to FIG. 28 (A)-(D). Done. As a result, the swinging body 312 swings around the shafts 314 and 316 in the receiving portion 310 through the guide groove 320 engaged with the guide boss 348.

Here, as shown in FIGS. 30A and 30B, a gap is formed in the receiving recess 324 between the tip of the plate portion 326 of the valve 321, so that the plate portion 326 is formed. Since a flow path 328 through which the silicone oil can pass along the swinging direction of the swinging body 312 is formed in the area to be accommodated, the rocking body 312 is pushed by the swinging body 312 when it swings. Silicone oil flows through the flow path 328 and is guided to an area opposite the traveling direction of the oscillator 312.

That is, due to the rocking of the rocking body 312, the viscous resistance caused by the rocking body 312 agitating the silicone oil and the rocking body 312 when the rocking body 312 oscillates in the containing portion 310 Shear resistance generated between the inner wall and the inner wall is generated, but since the compressive resistance compressed in the accommodating part 310 by the swinging of the swinging body 312 is small, the torque acting on the rotor 304 becomes small. Therefore, the damping force by the damper 300 is reduced.

On the other hand, when the rotor 304 is rotated at high speed, the viscous resistance caused by the silicone oil increases due to the high speed movement of the oscillator 312. As a result, the valve 321 in the oscillator 312 swings, and as shown in FIGS. 30C and 30D, one side of the pressure reducing passage 328 is blocked. Therefore, the silicone oil is compressed in the accommodating portion 310 by the oscillator 312 so that the compressive resistance is increased, thereby increasing the torque acting on the rotor 304, and thus the damping force by the damper 300. Will become large.

Here, when the rotation speed of the rotor 304 becomes slow and the viscosity resistance by silicone oil becomes small, the valve 321 oscillates and returns to an original position (center part of the accommodation recess 324). The torque acting on the rotor 304 returns to its original state.

That is, in this embodiment, the torque acting on this rotor 304 can be changed according to the rotational speed of the rotor 304. Moreover, by adjusting the rocking force of the valve 321, it is possible to easily change the rotational speed of the rotor 304 and the switching positions of low torque and high torque.

Further, by increasing the rotational speed of the rotor 304 through the gear 340 and converting it to the oscillation force of the oscillator 312, the movement amount of the oscillator 312 is increased with respect to the rotational movement amount of the rotor 304. Can be.

In addition, since the oscillators 312 are moved in phases with respect to each other, the oscillators 312 have different positions in the accommodating part 310. Accordingly, the torque generated for each accommodating portion 310 can be converted, so that the torque acting on the rotor 304 can be smoothly increased or decreased.

In the present embodiment, the frictional resistance due to the meshing contact between the large gear 354 and the gear 340, the sliding resistance when the guide boss 348 moves the guide groove 320, and the like also affect the torque of the rotor 304. Although it will work, since the torque acting by silicone oil is demonstrated here, the description about these is abbreviate | omitted.

As described above, the dampers according to these embodiments can be installed in sliding doors, wheels of wheelchairs, blinds, pet leads, piano covers, suit cases, glove boxes of automobiles, and the like, in addition to the drawing member. When the speed is greater than or equal to the predetermined value, the damping force by the damper increases through the rotor, so that the movement of the movable member can be slowed down.

In the present invention, the liquid chambers are in a non-communication state when the rotational speeds of the rotors are higher than or equal to a predetermined value, and the liquid chambers are in a communication state when the rotational speeds of the rotors are less than the predetermined value. It is not limited to the above embodiment.

1 is a sectional perspective view showing a damper according to a first embodiment of the present invention.

2 is an exploded perspective view showing a damper according to the first embodiment of the present invention.

3 is a cross-sectional view showing a damper according to the first embodiment of the present invention.

4A and 4B are plan views showing the operation of the inner member constituting the damper according to the first embodiment of the present invention.

5 is a perspective view illustrating a plate and a cap constituting the damper according to the first embodiment of the present invention.

FIG. 6: is a top view which shows the damper concerning 1st Embodiment of this invention, (A) is a figure which shows the state which the mutually adjacent spaces communicated, and (B) is a figure which shows the state where the mutually adjacent spaces are interrupted | blocked.

7 is a graph for explaining the action of the damper according to the first embodiment of the present invention.

8 is a graph for explaining the operation in a modification of the damper according to the first embodiment of the present invention.

9 is a perspective view showing a modification of the plate constituting the damper according to the first embodiment of the present invention.

10 is a perspective view showing a damper according to a second embodiment of the present invention.

11 is an exploded perspective view showing a damper according to a second embodiment of the present invention.

12 is a cross-sectional view illustrating a damper according to a second embodiment of the present invention.

Fig. 13 is a perspective view showing the relationship between the rotor and the chip constituting the damper according to the second embodiment of the present invention.

Fig. 14 is a sectional perspective view showing a damper according to a second embodiment of the present invention, showing a state where spaces adjacent to each other are in communication with each other.

Fig. 15 is a sectional perspective view showing a damper according to a second embodiment of the present invention, showing a state where spaces adjacent to each other are blocked.

Fig. 16 is a cross sectional view showing a damper according to a second embodiment of the present invention, in which (A) shows a state in which spaces adjacent to each other communicate with each other, and (B) shows a state in which spaces adjacent to each other are blocked.

17 is an exploded perspective view showing a damper according to a third embodiment of the present invention.

18 is an exploded perspective view showing a main portion of a damper according to a third embodiment of the present invention.

19 is a cross-sectional view illustrating a damper according to a third embodiment of the present invention.

20A and 20B are plan views illustrating positions of valves constituting the damper according to the third embodiment of the present invention.

Fig. 21 is a cross sectional view showing a damper according to a third embodiment of the present invention, in which (A) shows a state in which spaces adjacent to each other communicate with each other, and (B) shows a state in which spaces adjacent to each other are blocked.

It is sectional drawing explaining operation of the piston which comprises the damper concerning 3rd Embodiment of this invention.

Fig. 23 is an exploded perspective view showing a modification of the main portion of the damper according to the third embodiment of the present invention.

24A and 24B are plan views showing modifications of the valve constituting the damper according to the third embodiment of the present invention.

25 is an exploded perspective view showing a damper according to a fourth embodiment of the present invention.

Fig. 26 is a sectional view of a damper according to a fourth embodiment of the present invention.

27 is a plan view showing a damper according to the fourth embodiment of the present invention.

28A to 28D are plan views illustrating a relationship between a guide boss and a swinging body of a gear constituting the damper according to the fourth embodiment of the present invention.

Fig. 29 is an exploded perspective view showing the configuration of the lower surface of the oscillator that constitutes the damper according to the fourth embodiment of the present invention.

(B) and (D) are back views which show the operation | movement of the valve of the oscillator which comprises the damper concerning 4th Embodiment of this invention, (A) is sectional drawing of the AA line of (B), (C) is sectional view along the line B-B of (D)

Explanation of symbols on the main parts of the drawings

10-Damper 12-Housing

16-Trocoid Gear Shape (2nd Trocoid Gear Shape)

16A-Gear Section

18-Trocoid Gear Shape (1st Trocoid Gear Shape)

18A-Gear 20-Inner Member (Eccentric Member)

22-rotor

30-plate (first flow path blocking member, flow path variable stage)

56-torsion springs

100-Damper 102-Housing

104-Rotor 106-Cam groove (cam means)

108-collar (second flow path blocking member, flow path variable stage)

116-chip (moving member) 118-engaging protrusion (cam means)

122-chip housing (liquid chamber) 130-compartment rib (pillar)

137-coil spring (second fingering means, flow path variable stage)

200-Damper 202-Housing

208-Valve (3rd flow path blocking member, flow path variable stage)

212-Whirlpool pieces (third fingering means, flow variable stage)

214-Tension springs (third fingering means, flow path variable stages)

224-Piston Body (Swinging Element) 230-Piston Receptacle (Liquid Chamber)

242-Piston (Piston Member) 244-Rotor

300-Damper 302-Housing

304-Rotor 310-Receptacle (Liquid Chamber)

312-Oscillator 320-Guide Groove

321-Valve (closed member) 328-Flow path (decompression flow path)

338-Gear member (rotating member) 340-Gear

348-Guide boss (guide protrusion) S-Space (liquid chamber)

Claims (9)

Housings, A plurality of liquid chambers formed in the housing and filled with a viscous fluid; A rotating body rotatably received in the housing and receiving resistance from the viscous fluid of the liquid chamber; When the rotational speed of the rotating body is a predetermined value or more, the liquid chambers are in a non-communication state, and when the rotational speed of the rotating body is less than a predetermined value, the flow path that makes the liquid chambers in communication state has a variable stage. The damper characterized by the above-mentioned. The method according to claim 1, The rotating body, Rotor with the rotational force transmitted from the outside, An eccentric member which is eccentrically rotated with respect to the axial center of the rotor and constitutes the liquid chamber with the housing, The flow path variable stage, When the rotational speed of the rotor is more than a predetermined value, the first flow path blocking member to rotate by the shear force or the flow force of the viscous fluid generated between the rotor and the liquid chambers in a non-communication state, A position connected to the first flow path blocking member to hold the first flow path blocking member in a direction opposite to the rotational direction of the rotor and to bring the liquid chambers into communication when the rotation speed of the rotor is less than a predetermined value; And a first fingering means for returning the first flow path blocking member to the furnace. The method according to claim 2, The eccentric member has a first trocoid gear shape, a second trocoid gear shape engaging with the first trocoid gear shape is formed on an inner circumferential surface of the housing, the first trocoid gear shape and the second trocoid gear. The damper, characterized in that the liquid chamber is formed by a shape portion. The method according to claim 1 The rotating body, Rotor with the rotational force transmitted from the outside, A movable member disposed outside the rotor to form the liquid chamber between the housing and the housing; Cam means for converting the rotational force of the rotor to the movement in the direction along the axial direction of the rotor of the moving member, The flow path variable stage, When the rotational speed of the rotor is more than a predetermined value, the second flow path blocking member for rotating by the shear force generated between the rotor and the liquid chambers in a non-communication state, A position connected to the second flow path blocking member to hold the second flow path blocking member in a direction opposite to the rotation direction of the rotor, and when the rotation speed of the rotor is less than a predetermined value, the liquid chambers communicate with each other; And a second gripping means for returning the second flow path blocking member to the furnace. The method according to claim 4, The movable member protrudes from the inner wall of the housing and is installed to be movable between the pillar portions that partition the liquid chamber. The cam means is formed on the outer circumferential surface of the rotor, characterized in that it comprises a cam groove of the waveform having a peak and a curved portion in the axial direction of the rotor, and the engaging projection formed on the movable member and engaged with the cam groove Damper. The method according to claim 4 or 5, The moving member is a damper, characterized in that the engaging projection is engaged with the cam groove so as to move out of phase with each other. The method according to claim 1, The rotating body, Rotor with the rotational force transmitted from the outside, A rocking member which is eccentrically connected with respect to the axis center of the rotor in a state in which the central axis is inclined and oscillates by the rotation of the rotor; A piston member formed in the rocking member to form the liquid chamber between the housing and reciprocating by rocking of the rocking member, The flow path variable stage, A third flow path blocking member that rotates by a shear force generated between the rotor when the rotational speed of the rotor is greater than or equal to a predetermined value, and makes the liquid chambers non-communicating; A position connected to the third flow path blocking member to hold the third flow path blocking member in a direction opposite to the rotational direction of the rotor and to bring the liquid chambers into communication when the rotation speed of the rotor is less than a predetermined value; And a third gripping means for returning the third flow path blocking member to the furnace. Housings, A plurality of liquid chambers formed in the housing and filled with a viscous fluid; Rotors are transmitted from the outside, rotatably received in the housing and receiving resistance from the viscous fluid of the liquid chamber, A rotating member having a different axial center from that of the rotor and to which the rotating force of the rotor is transmitted A guide protrusion formed by shifting a position at an axis center of the rotating member, A linear guide groove engaging with the guide protrusion is formed, the oscillating body oscillating in the liquid chamber by the movement of the guide protrusion, A decompression flow path formed in the oscillator along the moving direction of the oscillator, and configured to communicate with the liquid chamber that is substantially divided with the oscillator interposed therebetween; And a blocking member formed on the oscillator, the blocking member moving by the viscous resistance caused by the viscous fluid to block the decompression flow path when the rotational speed of the rotor is greater than or equal to a predetermined value. The method according to claim 8, And the guide protrusion is engaged with the guide groove so that the oscillator moves out of phase with each other.

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