KR100774838B1 - Damper - Google Patents

Abstract

(Problem) The damper (moving distance) of a control valve body can be shortened, and the damper which is responsive is provided.

(Solution means) When the blade portion 14 is formed in an asymmetrical shape in the rotational direction with respect to a straight line extending radially from the small-diameter shaft portion 12S, and the rotor 11 rotates in the braking torque generating direction. The rotor 11 is made into the inclined surface 14s which inclined from the radial direction inner side to the radially rearward end side from the radial direction inner side to the radial direction outer side from the radial direction inner side to the radial direction outer side from the radial direction inner side, and the rotor 11 Is a plane 14f parallel to the straight line extending radially from the rear end side of the wing 14 positioned at the rear end side in the rotational direction when the motor rotates in the braking torque generation direction, and the inclined surface 14s. The inner side surface of the control valve body 21 which opposes is set as the parallel inclined surface 24s parallel to the inclined surface 14s, and the inner side surface of the control valve body 21 which faces the plane 14f is placed on the plane 14f. It is set as parallel parallel plane 25f.

Description

Damper {DAMPER}

1 is an exploded perspective view of a damper that is an embodiment of the present invention

(A) is a top view of the housing main body shown in FIG. 1, (b) is sectional drawing by the A-A line of FIG.

(A) is a top view of the cap shown in FIG. 1, (b) is sectional drawing by the B-B line | wire of FIG.

(A) is a top view of the rotor shown in FIG. 1, (b) is a right side view of the rotor shown in FIG. 1, (c) is a bottom view of the rotor shown in FIG. 1, (d) is FIG. Sectional drawing by the CC line of (b), (e) is cross sectioning by the DD line of FIG.

5 is an enlarged plan view of the control valve body shown in FIG. 1, (b) is an enlarged front view of the control valve body shown in FIG. 1, (c) is an enlarged rear view of the control valve body shown in FIG. (d) is sectional drawing by the E-E line | wire of FIG. 5 (b).

Figure 6 is a side view with a portion of the left side of the damper in one embodiment of the present invention

7 is an operation explanatory diagram

8 is an operation explanatory diagram

Explanation of symbols on the main parts of the drawings

D-Damper 1-Housing

2-housing body 3-engagement protrusion

4-bearing hole 5-pivoting wall

6-Cap 7-Through Hole

8-annular wall 11-rotor

12-Shaft 12S-Small Shaft

12B-Large Diameter Shaft 13-Protruding Shaft

14-Wings 14B-Pedestals

14D-wing body 14p-support surface

14s-Slope (front end side) 14f-Flat (rear end side)

15-Notch (distribution path) 16-Concave

17-Disk Flange 18-Air Check

21-control valve body 22-upper side wall

23-Lower side wall 24-Tip side wall (Tip side part)

24s-Parallel inclined plane (inner side) 25-Rear end side wall (rear end side part)

25f-Parallel plane (inside) 26-Cutout (pathway)

27-arc wall 28-protrusion wall

31-Viscous fluid 41-○ Ring

L-Straight line X-Braking torque generation direction

Y-direction of anti-braking torque

The present invention relates to a damper for generating braking torque only when the rotor rotates (or rotates) in a braking torque generating direction with respect to the housing.

The damper is a cylindrical housing, a rotor having radially formed on a portion of the cylindrical shaft portion and a portion of the shaft portion, and a wing portion formed axially on a portion of the shaft portion rotatably housed in the housing; A control valve body disposed between a portion of the shaft portion and covering the wing portion, and a viscous fluid filled in the housing, and the rotor rotates in the braking torque generating direction with respect to the housing, whereby the control valve body generates semi-braking torque with respect to the rotor. Direction, which causes the braking torque to be generated by closing the flow path of the viscous fluid, and the rotor rotates in the anti-braking torque generating direction with respect to the housing, whereby the control valve body moves in the braking torque generating direction with respect to the rotor. It is proposed to be in a non-braking state by opening the flow path of the viscous fluid.

[Patent Document 1] Japanese Patent No. 2882109

[Patent Document 2] Japanese Patent No. 3125416

[Patent Document 3] Japanese Patent No. 3053156

However, the above-described damper is formed by forming the wing portion in a shape symmetrical in the rotational direction with respect to a straight line extending radially from the shaft portion, forming the control valve body in a cross-sectional c-shape, and increasing the amount of movement of the control valve body. Since it is a way damper, the movement distance with respect to the rotor (wing part) of a control valve body becomes long when it is reversed from a braking state to a non-braking state, or from a non-braking state to a braking state.

Therefore, when reversing from the braking state to the non-braking state or from the non-braking state to the braking state, the clearance (moving distance) of the control valve body is long and the response is bad.

This invention is made | formed in order to eliminate the inconvenience as mentioned above, It is possible to shorten the clearance gap (moving distance) of a control valve body, and to provide the damper with a good responsiveness.

The present invention is as follows.

(1) a rotor having a cylindrical housing, a radially formed portion of a cylindrical shaft portion and a portion of the shaft portion, and a wing portion formed axially on a portion of the shaft portion rotatably housed in the housing; The control valve body is disposed between the housing and a part of the shaft portion and includes a control valve body covering the wing and a viscous fluid filled in the housing, and the rotor rotates in the direction of braking torque with respect to the housing. The braking torque is generated by moving in the anti-braking torque generating direction with respect to the rotor and closing the flow path of the viscous fluid, and the rotor rotates in the anti-braking torque generating direction with respect to the housing. The valve body moves in the direction of braking torque generation with respect to the rotor and the viscous fluid A damper that is in a non-braking state by opening a flow path, wherein the wing portion is formed in an asymmetrical shape in a rotational direction with respect to a straight line extending radially from the shaft portion, and the rotational direction when the rotor rotates in the braking torque generation direction. The inclined surface inclined from the radially inner side to the radially outer side from the radially inner side toward the radially outer side from the radially inner side to an inclined surface inclined from the radially inner side to the rearward end side, and the rotor rotates in the braking torque generating direction. The rear end side side of the wing portion located on the rear end side is a plane parallel to the radially extending straight line, and the inner side surface of the control valve body facing the inclined surface is a parallel inclined plane parallel to the inclined surface. Parallel to the plane the inner surface of the control valve element opposite the plane It is characterized by the parallel plane.

(2) The damper according to (1), wherein a width orthogonal to the axis of the shaft portion of the tip side portion of the control valve body having the parallel inclined surface is widened from the radially inner side to the radially outer side. It is done.

(3) The damper according to (1) or (2), wherein a protruding wall extending in the circumferential direction is formed at the tip end side portion of the control valve body having the parallel inclined surface.

(4) The damper according to (3), wherein the protruding wall is in contact with the inner circumferential surface of the housing.

(5) The damper according to (1), wherein the thermal expansion coefficient of the control valve body is set to be equal to or less than the thermal expansion coefficient of the housing or the rotor.

(The best form to carry out invention)

EMBODIMENT OF THE INVENTION Hereinafter, the Example of this invention is described based on drawing.

Figure 1 is an exploded perspective view of a damper according to an embodiment of the present invention, Figure 2 (a) is a plan view of the housing body shown in Figure 1, Figure 2 (b) is a cross-sectional view taken along line AA of Figure 2 (a), Figure 3 ( a) is a plan view of the cap shown in FIG. 1, FIG. 3 (b) is a sectional view taken along line BB of FIG. 3 (a), FIG. 4 (a) is a plan view of the rotor shown in FIG. 1, and FIG. 4 (b) is Fig. 4 (c) is a bottom view of the rotor shown in Fig. 1, Fig. 4 (d) is a sectional view taken along line CC of Fig. 4 (b), and Fig. 4 (e) is shown. 5B is an enlarged plan view of the control valve body shown in FIG. 1, and FIG. 5B is an enlarged front view of the control valve body shown in FIG. c) is an enlarged rear view of the control valve body shown in FIG. 1, FIG. 5 (d) is a sectional view taken along line EE of FIG. 5 (b), and FIG. 6 is a section of the left side of the damper according to an embodiment of the present invention in cross section. 7 and 8 are operational explanatory views.

In FIG. 1, the damper D has a cylindrical housing 1, a rotor 11 rotatably received within the housing 1, and between the rotor 11 and the housing 1. Viscous between the control valve body 21 disposed on the housing 21 and the viscous fluid 31 (see FIG. 6) such as silicone oil and grease filled in the housing 1, and the housing 1 and the rotor 11. The ring 31 is configured to prevent the fluid 31 from leaking out.

Moreover, the housing 1, the rotor 11, and the control valve body 21 are shape | molded by mixing 50 mass% of polyamide and glass fiber.

As shown in FIG. 1, the housing 1 includes the housing main body 2 and a cap 6 that closes the opening of the housing main body 2.

As shown in Figs. 1 and 2, the housing main body 2 has a cylindrical shape which is narrowed toward the bottom as a truncated conical main surface which is slightly inwardly inclined after the ceiling is opened (opened) and the inner circumferential surface is lowered from the circumferential surface. An engaging protrusion 3 is formed so as not to protrude to the outside of the radial main surface passing through the center on the outer side of the bottom, and a bearing hole for rotatably supporting the rotor 11 at the inner center of the bottom ( 4) is formed, and rotationally restricting walls 5, 5 extending from the bottom to the lower side slightly above the upper end and facing at predetermined intervals are formed at symmetrical positions of the inner circumference.

1 and 3, a through hole 7 through which the rotor 11 rotatably penetrates is formed in the center of the cap 6, and an annular shape is formed around the lower side of the through hole 7. The wall 8 is formed.

As shown in Figs. 1 and 4 (b), the rotor 11 is formed around the cylindrical shaft portion 12 and the shaft portion 12 and inserted into the housing main body 2. It is comprised by the disk-shaped flange 17. As shown in FIG.

And the shaft part 12 is the small diameter shaft part 12S made into the height of the rotation restricting wall 5 and 5 formed in the housing main body 2, as shown to FIG. 1 and FIG. 4 (b), and this small diameter shaft part. Concentric with 12S, it consists of the large diameter shaft part 12B which continues in the upper side of the small diameter shaft part 12S, and becomes I cut shape from the middle to the upper end part.

In the small-diameter shaft portion 12S described above, as shown in FIG. 1 or 4, a protruding shaft 13 rotatably supported by the bearing hole 4 of the housing body 2 is formed at the center of the bottom, and the outer circumference thereof is formed. Wing portions 14, 14 extending in the axial direction are formed at symmetrical positions of.

And as shown to FIG.4 (c)-FIG.4 (d), the wing | blade part 14 is the pedestal-shaped pedestal part 14B which expands outward in a planar view, and the outer side of this pedestal part 14B. It is comprised by the wing part main body 14D arrange | positioned so that the support surface 14p along the outer periphery of the pedestal part 14B may be formed.

As shown in Fig. 4D, the pedestal portion 14B is symmetric in the rotational direction with respect to the straight line L extending radially from the small-diameter shaft portion 12S.

And as shown in FIG.4 (d), the wing | blade part main body 14D is formed in the shape which is asymmetric in the rotation direction with respect to the straight line L extended radially from the small diameter shaft part 12S, and the rotor 11 (14s) inclined from the radially inner side to the radially outer side from the radially inner side toward the radially rearward end side from the radially inner side from the radially inner side to the radially outward side when the rotor rotates in the braking torque generating direction. When the rotor 11 rotates in the braking torque generating direction, the rear end side side located at the rear end side in the rotational direction is in a plane 14f parallel to the straight line L extending radially. It is.

Moreover, the notch 15 which forms the flow path of the viscous fluid 31 is formed in the wing | blade main body 14D, as shown to FIG. 1, FIG. 4 (b) and FIG. 4 (e).

Then, as shown in Figs. 1, 4 (b) and 4 (e), the small diameter shaft portion 12S has the rear side of the notch 15 when the rotor 11 rotates in the control torque generating direction. The groove base-shaped recessed part 16 of the baseball part which extends in the anti-braking torque generation direction Y from the wing part 14 is formed in the part located in this.

In addition, the disk-shaped flange 17 is formed in the outer periphery of the lower end part of the large diameter shaft part 12B, as shown to FIG. 1 and FIG. 4 (b), and FIG. 1, FIG. 4 (a) and FIG. 4 (c). As shown in the figure, pneumatic notches 18 and 18 are formed at symmetrical circumferential positions.

1 and 5 (c), the control valve body 21 has an upper side wall 22, a lower side wall 23, and the rotor 11 in a braking torque generating direction. To the tip end side wall 24 as the tip end side portion located at the tip end side in the rotational direction when rotating, and the rear end positioned at the rear end side in the rotational direction when the rotor 11 rotates in the braking torque generating direction. It is comprised so that the wing part main body 14D of the rotor 11 may be covered by the rear end side wall 25 as a side part, and the circular arc wall 27 which contact | connects the inner peripheral surface of the housing main body 2. As shown in FIG.

Then, as shown in Fig. 1, Fig. 5A and Fig. 5D, the distal end side wall 24 has a rotation direction distal end when the rotor 11 rotates in the braking torque generating direction. A protruding wall 28 extending in the circumferential direction of the side and in contact with the inner circumferential surface of the housing main body 2 is formed.

As shown in FIG.5 (d), the said end part side side wall 24 has the width orthogonal to the axis | shaft of the shaft part 12 (of a cross section) becoming wider from radial direction inner side to radial direction outer side.

And the inner side surface which opposes the inclined surface 14s of the blade | wing part 14 of the tip side wall 24 is parallel to the inclined surface 14s, as shown in FIG.5 (d), and the parallel inclined surface which contact-deviates ( 24s).

Moreover, the inner side surface which opposes the plane 14f of the blade | wing part 14 of the rear side side wall 25 is parallel to the plane 14f, and as shown in FIG. 25f).

In addition, in the rear end side wall 25, as shown in Figs. 1, 5 (c) and 5 (d), a cutout 26 forming a flow path of the viscous fluid 31 is formed by a wing portion ( It is formed to correspond to the notch 15 of 14).

And the thickness of the upper side wall 22 is made into the space | interval of the blade | wing part 14 and the disk-shaped flange 17, and the thickness of the lower side wall 23 is larger than the thickness of the upper side wall 22, and a control valve body ( 21) prevents incorrect mounting.

The outer circumferential surfaces of the arc walls 27 and the protruding walls 28 are conical circumferential surfaces that contact the inner circumferential surfaces of the housing body 2.

Next, an example of assembly is demonstrated.

First, the housing main body 2 is fixed with the open end (opening) side upward, and an appropriate amount of viscous fluid 31 is injected into the housing main body 2.

Then, the ring 41 is fitted to the disk-shaped flange 17 on the large-diameter shaft portion 12B, and the viscous fluid 31 is disposed on the lower surface of the small-diameter shaft portion 12, the disk-shaped flange 17, and the control valve body 21. ), And attaching the control valve bodies 21 and 21 to the wing portions 14 and 14 to cover the wing body bodies 14D and 14D, and then into the housing body 2 from the protruding shaft 13 side. Insert the shaft portion (12).

When the shaft portion 12 is inserted into the housing main body 2 in this manner, the protruding shaft 13 is rotatably fitted in the bearing hole 4, and the disk-shaped flange 17 is rotated by the restricting walls 5, 5. In addition to contacting the upper surface of the c), the air of the portion partitioned by the housing main body 2 and the disk-shaped flange 17 escapes from the pneumatic cuts 18 and 18.

Next, the ring 41 is deformed by inserting the large-diameter shaft portion 12B into the through hole 7 with the annular wall 8 downward, by lowering the cap 6 and pressing it to a predetermined pressure. The viscous fluid 31 is prevented from leaking between the housing 1 and the rotor 11, and the opening of the housing main body 2 is closed by the cap 6.

In this state, the damper D can be assembled as shown in FIG. 6 by welding and sealing the upper end of the housing main body 2 and the outer periphery of the lower surface of the cap 6 so as to be surrounded by, for example, high frequency welding. Can be terminated and assembly.

When the damper D is assembled, the rotation restricting walls 5 and 5 in the housing 1 are divided into two by the wing portions 14 and 14 and the control valve bodies 21 and 21.

Next, the operation will be described with reference to FIGS. 7 and 8.

In addition, the damper D shall be fixed so that the housing 1 may not rotate by the engagement protrusion 3.

First, as shown in FIG. 7, when a force for rotating the rotor 11 in the braking torque generating direction (clockwise) acts on the large-diameter shaft portion 12B, the blade 14 also generates braking torque. Rotate simultaneously in the direction.

However, since the control valve body 21 covering the wing main body 14D is subjected to the resistance of the viscous fluid 31, the inclined surface 14s is in contact with the parallel inclined surface 24s and is distal to the tip body 14D by the wing main body 14D. When the side wall 24 is pressed down, it rotates with the blade | wing part 14, as shown in FIG.

In this way, when the inclined surface 14s is in contact with the parallel inclined surface 24s and the wing body 14D is in contact with the tip side wall 24, the notch 15 is closed by the tip side wall 24. The viscous fluid 31 in the division of the right side (tip side side wall 24 side) than the wing | blade part 14 in 7 is pressurized, and this pressurized viscous fluid 31 pushes the protruding wall 28 into a housing main body. It is pressed by the inner peripheral surface of (2).

Therefore, the pressurized viscous fluid 31 passes through the orifice of the housing main body 2, the disk-shaped flange 17, the wing | blade part 14, and the control valve body 21, and the left side rather than the wing | blade part 14 is carried out. Since it flows into the compartment of the {side end side wall 25 side}, the rotor 11 is rotated clockwise.

Next, as shown in FIG. 8, when the force which makes the rotor 11 rotate to anti-braking torque generation direction Y (counterclockwise direction) acts on the large diameter shaft part 12B, also the wing part 14 also acts. Rotate simultaneously in the anti-braking torque generation direction (Y).

However, since the control valve body 21 covering the wing body 14D is subjected to the resistance of the viscous fluid 31, the plane 14f is brought into contact with the parallel plane 25f, and is separated by the wing body 14D. When the end side side wall 25 is pressed, it rotates with the blade part 14, as shown in FIG.

In this way, when the plane 14f is in contact with the parallel plane 25f and the wing body 14D is in contact with the rear end side wall 25, the cutouts 15 occluded by the front end side wall 24 are opened. The space between the inclined surface 14s and the parallel inclined surface 24s is sufficiently secured by the inclined surface 14s and the parallel inclined surface 24s being parallel.

Accordingly, the viscous fluid 31 in the section on the left side (the rear side side wall 25 side) is pressurized from the wing 14 in FIG. 8, and the pressurized viscous fluid 31 is flowed through (cutting). (26), the notch 15 passes between the wing 14 and the tip end side wall 24} and flows into the compartment on the right side (the tip side side wall 24 side) from the wing 14, Braking is hardly applied to the rotation of the electrons 11 counterclockwise.

As described above, according to an embodiment of the present invention, the blade 14 is formed in a shape asymmetrical in the rotational direction with respect to the straight line L extending radially from the small diameter shaft portion 12S, and the rotor 11 ) Is rotated in the direction of the braking torque generation, the side of the tip side of the wing 14 (the wing body 14D) located on the tip side of the rotational direction is rotated from the radially inner side to the radially outer side. Wing part 14 (wing part) which is set to the inclined surface 14s inclined from the front end side to the rear end side in the rotational direction, and located at the rear end side in the rotational direction when the rotor 11 rotates in the braking torque generating direction. The rear end side side of the main body 14D is a plane 14f parallel to the radially extending straight line L, and the inner surface of the control valve body 21 facing the inclined surface 14s is the inclined surface 14s. Inside of the control valve body 21 facing parallel plane 14f as a parallel inclined surface 24s parallel to Since the side surface is made into the parallel plane 25f parallel to the plane 14f, even if the movement distance with respect to the rotor 11 (wing part 14) of the control valve body 21 is shortened, Enough channel can be secured.

Therefore, the clearance of the control valve body 21 can be shortened and response will be improved.

Since the width orthogonal to the axis of the shaft portion 12 of the tip end side portion of the control valve body 21 having the parallel inclined surface 24s was widened from the radially inner side to the radially outer side, the housing The length of the circumferential direction of the control valve body 21 which contacts the inner peripheral surface of (1) becomes long, the attitude | position of the control valve body 21 is stabilized, and operation | movement is stabilized.

Moreover, since the protruding wall 28 extended in the circumferential direction was formed in the front end side part of the control valve body 21 which has the parallel inclined surface 24s, the pressurized viscous fluid 31 in a braking state protrudes. By pressing 28 in the radial direction, the control valve body 21 is pressed against the inner circumferential surface of the housing 1, whereby the attitude of the control valve body 21 becomes more stable.

In addition, since the protruding wall 28 is brought into contact with the inner circumferential surface of the housing 1, the attitude of the control valve body 21 is further stabilized.

In addition, since the coefficient of thermal expansion of the control valve body 21 is the same as that of the housing 1 and the rotor 11, even if the temperature rises and the viscosity of the viscous fluid 31 decreases, the orifice (housing 1) ), The gap between the control valve body 21 and the gap between the rotor 11 and the control valve body 21 can be reduced, so that fluctuations in the braking torque can be suppressed.

In the above embodiment, the thermal expansion coefficient of the control valve body 21 is shown to be the same as the thermal expansion coefficient of the housing 1 and the rotor 11, but the thermal expansion coefficient of the control valve body 21 is shown in the housing. The same effect can be acquired even if it is below the thermal expansion coefficient of (1) or the rotor 11.

Moreover, although the example of the damper D whose rotation range of the rotor 11 is 180 degrees or less was shown, the damper which rotates 360 degrees or more can be made by removing the rotation restricting walls 5 and 5.

According to the present invention, the blade portion is formed in an asymmetrical shape in the rotational direction with respect to the straight line extending radially from the shaft portion, and radiates the tip side side of the wing portion positioned on the tip side of the rotation direction when the rotor rotates in the braking torque generation direction. The inclined surface inclined from the inner side in the direction of rotation to the rear end in the direction of rotation direction from the front end side in the radial direction, and the rear end side side of the wing portion positioned at the rear end side in the rotation direction when the rotor rotates in the braking torque generation direction, A plane parallel to the radially extending straight line is used, and the inner surface of the control valve body opposing the inclined surface is a parallel inclined plane parallel to the inclined surface, and the inner surface of the control valve body opposing the plane is a parallel plane parallel to the plane. Therefore, even if the moving distance with respect to the rotor (wing part) of a control valve body is shortened, a viscous fluid It can be secured to the distributor enough.

Therefore, the clearance of the control valve body can be shortened and the response is improved.

And since the width | variety orthogonal to the axis | shaft of the shaft part of the front end side part of a control valve body which has a parallel inclined surface was made wider from radial direction inner side to radial direction outer side, the length of the circumferential direction of the control valve body which contact | connects the inner peripheral surface of a housing Lengthens, the attitude of the control valve body is stabilized, and the operation is stabilized.

Further, since a protruding wall extending in the circumferential direction is formed at the tip end side portion of the control valve body having the parallel inclined surface, the pressurized viscous fluid in the braking state presses the protruding wall in the radial direction so that the control valve body is in the inner circumferential surface of the housing. , The posture of the control valve body is further stabilized.

Further, since the protruding wall is brought into contact with the inner circumferential surface of the housing, the attitude of the control valve body is further stabilized.

In addition, since the coefficient of thermal expansion of the control valve body is equal to or less than the coefficient of thermal expansion of the housing or the rotor, even if the temperature rises and the viscosity of the viscous fluid decreases, the orifice (gaps between the housing and the control valve body and between the rotor and the control valve body) By narrowing, the fluctuation in the braking torque can be suppressed.

Claims (5)

Cylindrical housing, A rotor formed radially on a portion of the cylindrical shaft portion and a portion of the shaft portion, and a wing portion formed axially on the portion of the shaft portion rotatably housed in the housing; A control valve body disposed between the housing and a portion of the shaft portion and covering the wing portion; A viscous fluid filled in the housing, When the rotor rotates with respect to the housing in a braking torque generation direction, the control valve body moves in a direction of anti-braking torque generation with respect to the rotor to close the flow path of the viscous fluid to generate a braking torque. , As the rotor rotates in the anti-braking torque generating direction with respect to the housing, the control valve body moves in the braking torque generating direction with respect to the rotor to open the flow path of the viscous fluid, thereby becoming a non-braking state. The wing portion is formed in a shape asymmetrical in the rotational direction with respect to the straight line extending radially from the shaft portion, When the rotor rotates in the braking torque generating direction, the side of the tip end side of the wing positioned at the tip end side of the rotational direction is an inclined surface inclined from the radial direction outward side to the radial direction rear end side from the radial direction inner side. , When the rotor rotates in the braking torque generating direction, the rear end side side of the wing positioned at the rear end side in the rotational direction is a plane parallel to the straight line extending radially, The inner side surface of the control valve body facing the inclined surface is a parallel inclined surface parallel to the inclined surface, In making the inner surface of the said control valve body which opposes the said plane into the parallel plane parallel to the said plane, A damper, characterized in that a protruding wall extending in the circumferential direction is formed at a tip end side portion of the control valve body having the parallel inclined surface. The method according to claim 1, The damper characterized by the width | variety orthogonal to the axis | shaft of the said shaft part of the front-end | tip part part of the said control valve body which has the said parallel inclined surface spreading radially outward from the radial direction inner side. delete The method according to claim 1, And the protruding wall is in contact with the inner circumferential surface of the housing. The method according to claim 1, A damper, characterized in that the thermal expansion coefficient of the control valve body is equal to or less than the thermal expansion coefficient of the housing or the rotor.

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