JPH079255B2 - Actuator built-in type shock absorber - Google Patents

Description

Description: [Object of the invention] [Industrial field of application] The present invention relates to a shock absorber used in an automobile or the like, and in particular, for example, an actuator including an actuator for adjusting its damping force therein. Regarding a built-in shock absorber.

[Prior Art] For example, in a suspension mechanism of an automobile, the steering stability and riding comfort of the automobile greatly change depending on the magnitude of its vibration absorbing force. However, in many cases, steering stability and riding comfort are determined by contradictory factors, so if you set the vibration absorption force with emphasis on steering stability, the riding comfort will worsen, and the riding comfort will be emphasized. When setting the force, the steering stability deteriorates. Therefore, the degree of harmony between the driving stability and the riding comfort should be determined according to the user's request, driving environment, and the like.

Therefore, the shock absorber used in the recent suspension mechanism has a structure in which the damping force can be adjusted in about three stages. Further, an actuator including an electric motor for adjusting the damping force is provided inside the shock absorber so that the adjustment can be electrically controlled. Specifically, a rotary valve for adjusting the flow rate of fluid flowing between an upper chamber and a lower chamber separated by a piston is provided, and a drive shaft of an electric motor is connected to a shaft of the valve.

However, although the shock absorber is filled with oil, a general electric motor cannot be immersed in oil. Therefore, conventionally, an O-ring is provided on the outer circumference of a drive shaft connecting the electric motor and the rotary valve to separate the electric motor and the rotary valve to prevent oil leakage.

[Problems to be Solved by the Invention] However, when the O-ring is provided, a relatively large frictional force is generated between the O-ring and the outer periphery of the drive shaft. In particular,
When the oil pressure is high, the rotary valve receives a force in a direction orthogonal to the axial direction, and the force pushes the drive shaft in a specific direction of the O-ring, increasing the frictional force between them. Therefore, in order to reliably drive the rotary valve, a large driving force is required, so that a large electric motor has to be used and power consumption also increases.

Further, in this case, when the O-ring wears, oil leakage occurs, so that the durability is low.

An object of the present invention is to provide a shock absorber with a built-in actuator that has high durability and can drive a rotary valve and the like with a small driving force.

[Structure of the Invention] [Means for Solving the Problems] In order to achieve the above object, in the present invention, a space in which an adjusting mechanism for adjusting the damping force of a shock absorber and the like is arranged, and an electrical space for driving the space are provided. A driving force generated by the electric driving means by completely separating the space in which the driving means is arranged by the separating means made of a non-magnetic material and magnetically coupling the movable part of the adjusting means and the electric driving means. To the adjustment mechanism.

[Operation] According to this, the separating means for separating the space in which the adjusting mechanism is arranged from the space in which the electric driving means is arranged is not in contact with the movable portion of the adjusting mechanism and the electric driving means. Good. Therefore, the movable portion of the adjusting mechanism is not subjected to the frictional force by the separating means, and the movable portion can be sufficiently driven with a small driving force. Moreover, since the separating means does not wear, there is no risk of oil leakage from the space on the adjusting mechanism side to the space on the electric driving means side, and the durability is high.

When magnetically coupling the movable part of the adjusting means and the electric driving means, a permanent magnet is provided in the movable part of the adjusting means, and an electric coil for generating a rotating magnetic field is arranged outside the separating means surrounding the permanent magnet. For example, the movable part of the adjusting means can be rotated by energizing the electric coil. However, in this way, since the movable part, the separating means and the electric coil are coaxially arranged, the diameter of that part becomes large,
The external shape of the shock absorber becomes large (thick).

Therefore, in the present invention, the drive source body of the electric drive means is arranged at a position on the extension line of the rotary shaft of the movable part of the adjusting mechanism, and at least a part thereof is connected to the drive shaft at the outer peripheral position of the movable part. The permanent magnet supported by the extending support member is arranged at a position facing the permanent magnet of the adjusting mechanism. By doing so, the shape of the portion connecting the adjusting mechanism and the electric drive means becomes small, and the diameter of the shock absorber can be made small.

Further, in this type of device, in order to position the movable part, a regulating member that is generally in contact with the movable part is provided, but if this type of regulating member is provided, wear will occur due to contact with the movable part, It is easy to cause failure and malfunction. Further, when the regulation member is provided, the rotation range of the movable member is narrowed.

Therefore, in the present invention, a positioning means (rotation restriction ring 164) including a magnetic body having irregularities formed in accordance with a predetermined rotational position of the movable part is fixed to the outside of the permanent magnet of the electric drive means. However, by this positioning means,
The rotation of the movable portion is restricted at a predetermined rotation position. With this configuration, the rotation of the movable portion can be restricted by a magnetic force at a specific position in a non-contact manner, so that no abrasion occurs and the movable portion can be rotated 360 degrees.

Other objects and features of the present invention will become apparent from the following description of embodiments with reference to the drawings.

[Embodiment] FIG. 3 shows the overall structure of a shock absorber of one type for carrying out the present invention. Please refer to FIG. Generally speaking, the casing of this shock absorber is composed of an inner cylinder 2 and an outer cylinder 3 which are coaxially arranged. Inside the inner cylinder 2,
The rod 1 is inserted. A piston mechanism 200 is connected to one end of the rod 1. The inside of the rod 1 is hollow, and the internal space of the rod 1 is provided with an actuator mechanism 100 coupled to the piston mechanism 200. The electrical cable for the actuator mechanism 100 is
It is pulled out from a to the outside of the shock absorber.

The inner space of the inner cylinder 2 is divided into a piston upper chamber 9 and a piston lower chamber 10 by a piston mechanism 200. The piston upper chamber 9 and the piston lower chamber 10 are filled with hydraulic oil 14. As will be described later, the piston mechanism 200 is formed with a flow path including an orifice and a valve, and the working oil 14 can move between the piston upper chamber 9 and the piston lower chamber 10.

A base valve mechanism 300 is provided at one end of the lower piston chamber 10. The base valve mechanism 300 regulates the movement of fluid between the inner space 10 of the inner cylinder 2 and the inner space 11 of the outer cylinder 3. The base valve mechanism 300 is provided with the gas charging port 12.
The inner space 11 of the outer cylinder 30 is filled with nitrogen gas 7.
In addition, 4 is a lower seat that supports one end of a coil spring (not shown), 5 is a guide member that guides the rod 1, and 6
Is a seal, 8 is a spindle, and 13 is a connector.

The structure of the actuator mechanism 100 of FIG. 3 is shown in detail in FIG. 1, and the IIa-IIa line cross section and the IIb-IIb line cross section of FIG. 1 are shown in FIGS. 2a and 2b, respectively. Moreover, the different states of the cross section taken along the line IV-IV of FIG. 1 are shown in FIGS.
Shown in Figures 4b, 4c and 4d.

First, a description will be given with reference to FIG. 201 is a rotary valve body for adjusting the damping force of the shock absorber. The valve body 201 has a columnar shape, is supported by a rod 162, and is rotatable about an axis. Two permanent magnets 158a and 158 are provided at one end 201a of the valve body 201.
b is stuck. The permanent magnets 158a and 158b are fixed to each other, and one surface has an N pole and the other has an S pole on the surface opposite to the fixed surface.

To cover the one end 201a of the valve body and the permanent magnets 158a and 158b,
A cap 157 is arranged. The cap 157 is made of a non-magnetic material, has a slightly larger diameter than the valve body 201, and is not in contact with the valve body 201 and the permanent magnets 158a and 158b. The opening of the cap 157 is in contact with the inner wall surface 162a of the rod 162, and the rod 1 is fixed by a fixing ring 159 press-fitted between the inner wall surface of the rod 162 and the outer circumference of the cap 157.
It is stuck to 62. The O-ring 160 seals so that the fluid inside the cap 157 does not flow to the outside.

The electric motor 151 is a DC motor, and its drive shaft has both ends projecting to the outside of the motor. A magnet holder 154 is attached to one end 151a of the drive shaft via a support member 153. Magnet holder 154
The shape of the magnet holder is such that the inner diameter is slightly larger than the outer diameter of the cap 157.
154 is arranged so as to cover the outer circumference of the cap.

The magnet holder 154 is a non-magnetic material, and permanent magnets 155 and 156 are fixedly held in two grooves formed on the inner peripheral surface thereof (see FIG. 2a). One of the permanent magnets 155 has the surface exposed on the inner peripheral surface of the magnet holder 154 magnetized to the S pole, and the other permanent magnet 156 has
The surface exposed to the inner peripheral surface of the magnet holder 154 is magnetized to the N pole.

That is, the N pole of the permanent magnet 158a and the S pole of the permanent magnet 155 are opposed to each other via the cap 157 made of a non-magnetic material, and the S pole of the permanent magnet 158b and the N pole of the permanent magnet 156 are interposed via the cap 157. Are facing each other. Therefore, attractive forces are generated between the permanent magnets 158a and 155 and the permanent magnets 158b and 156, respectively.

That is, when the electric motor 151 is driven, the permanent magnets 155 and 156 are rotated by the rotation of the shaft thereof, the permanent magnets 158a and 158b attracted to them rotate together with the permanent magnets 155 and 156, and the valve body 201 also rotates. Therefore, although the valve body 201 and the electric motor 151 are mechanically separated, the electric motor 1
The driving force of 51 is transmitted to the valve body 201 via magnetic force.

Further, as shown in FIG. 2b, a rotation restriction ring 164 is arranged on the outer circumference of the permanent magnets 155 and 156. The rotation restriction ring 164 is made of a magnetic material, and convex portions 164a and concave portions 164b are alternately formed. Six convex portions and concave portions are formed, and the length of each convex portion and each concave portion is about 1/12 of the circumferential length of the rotation restricting ring.

The rotation restriction ring 164 is fixed to the inner wall surface of the rod 162. The concave portion 164b of the rotation restriction ring is the permanent magnet 155 or 156.
When facing each other, the distance between them is shorter than that of the convex portion 164a, so that a large magnetic attraction force acts between them. Convex 16
When 4a faces the permanent magnets 155 and 156, the magnetic attraction force between them is much smaller than that in the case of the recess.

Therefore, even if the permanent magnets 155 and 156 are positioned at the positions facing the respective convex portions 164a of the rotation restricting ring, the concave portion 164b and the permanent magnet adjacent to the convex portion 164a are adjacent to the convex portion 164a.
Since the magnetic attraction force between the permanent magnets 155 and 156 is larger, the permanent magnets 155 and 156 rotate further and stand still at a position where they face the recess 164b of the rotation restriction ring.

That is, the permanent magnets 155 and 156 are automatically positioned by the rotation restriction ring 164 at six predetermined positions (angles). In practice, the permanent magnets 155 and 156 are mainly positioned by another mechanism, and the rotation restriction ring 164
Serves to hold the position of the permanent magnet.

The support member 1 is attached to the other end 151b of the drive shaft of the electric motor 151.
25 is stuck. Two stopper plates 123 and 124 are mounted on the outer periphery of the support member 125. One stopper plate 123 is rotatable with respect to the support member 125, and the other stopper plate 124 is fixed to the support member 125.

As shown in FIGS. 4a to 4d, the stopper plate 123
Is supported by the support member 125 at its central portion. The stopper plate 124 has a fan shape having a predetermined spread, and one end thereof is supported by the support member 125. On the stopper plate 124, two protrusions 124a and 124b are formed so as to surround one end of the stopper plate 123. Since the protrusions 124a and 124b are formed at positions where they engage with the stopper plate 123, the range (angle) of relative movement between the stopper plates 123 and 124 is regulated to be smaller than the spread angle of the fan of the stopper plate 124. .

Referring again to FIG. 1, the solenoid mechanism 110 is provided on the left side of the electric motor 151. Two fixed cores 1
12 and 117 are arranged apart from each other, and an electric coil 113 is wound around a coil bobbin 114 arranged outside them. The core 112 is hollow, and the plunger 111 is inserted into the core 112 so as to be movable in the axial direction.

The pin 115 has one end fixed to the plunger 111 and the other end movably supported by a core 117. Also pin 1
A movable plate 120 is fixed to the other end of 15. A compression coil spring 116 is provided between the plunger 111 and the core 117.
And the plunger 111 is constantly subjected to a force toward the left side in FIG. 1 by the spring 116.

Therefore, when the electric coil 113 is not energized, the plunger 111 is positioned in the state shown in FIG. 1, and when the electric coil 113 is energized, the plunger 111 moves to the right and one end of the plunger 111 contacts one end of the core 117. Be positioned at.
The movable plate 120 fixed to the plunger 111 moves in the axial direction of the shock absorber together with the plunger 111 according to the bias / de-energization of the electric coil 113.

The solenoid mechanism 110 is supported by a frame 161 of the actuator mechanism via a plate 118.

As shown in FIG. 4a, two fixed stoppers 122 and 126 are fixed to the plate 118. These fixed stoppers 122, 126 are made of rubber, and one end of each of them is projected to a position where they engage with the stopper plate 123. The two fixed stoppers 122 and 126 are positioned so as to surround the stopper plate 123.

A columnar stopper pin 121 is fixed to one end of the movable plate 120. In the state shown in FIG. 1, that is, when the electric coil 113 is not energized, the stopper pin 121
Is in the retracted position where it does not engage with the stopper plate 123, but when the electric coil 113 is energized, the stopper pin 121
It moves to the right in FIG. 1 and is positioned to engage with the stopper plate 123, as shown in FIG. 4b.

Therefore, when the actuator mechanism 100 is in the state shown in FIG. 4a, if the electric coil 113 is de-energized and the electric motor 151 is driven clockwise in FIG.
When rotated by an angle of θ, as shown in FIG. 4d, the protrusion 124b of the stopper plate 124 contacts one end of the stopper plate 123, and the stopper plate 123 and the other end contact the fixed stopper 126. The drive shaft 151b stops rotating and is positioned at that angle.

Further, when the actuator mechanism 100 is in the state shown in FIG. 4d, the electric coil 113 is de-energized and the electric motor 151 is moved to the first position.
If it is driven counterclockwise in Fig. 4d, its drive shaft will move to 2
When rotated by an angle of θ, as shown in FIG. 4a, the protrusion 124a of the stopper plate 124 contacts one end of the stopper plate 123 and the other end of the stopper plate 123 contacts the fixed stopper 122. The drive shaft 151b stops rotating and is positioned at that angle.

Further, when the actuator mechanism 100 is in the state shown in FIG. 4a, when the electric coil 113 is energized to drive the electric motor 151 in the clockwise direction in FIG. 4a, when the drive shaft rotates at the angle θ, the 4b Stopper plate as shown
The protrusion 124b of 124 abuts on one end of the stopper plate 123,
The other end of the stopper plate 123 comes into contact with the stopper pin 121, and the drive shaft 151b stops rotating and is positioned at that angle.

Further, when the actuator mechanism 100 is in the state shown in FIG. 4d, when the electric coil 113 is energized to drive the electric motor 151 clockwise in FIG. 4d, when the drive shaft rotates at an angle of θ, As shown in FIG. 4c, the protrusion 124a of the stopper plate 124 contacts one end of the stopper plate 123, the other end of the stopper plate 123 contacts the stopper pin 121, and the drive shaft 151b stops rotating. Positioned at that angle.

That is, the state of the actuator mechanism 100 is as shown in FIG.
It is set to any one of the four types shown in Fig. 4b, Fig. 4c and Fig. 4d. In the state shown in FIG. 4b and the state shown in FIG. 4c, the angle of the drive shaft of the electric motor 151 is the same. That is, the projection 124b of the stopper plate 124 contacts one end of the stopper plate 123 and the other end of the stopper plate 123 contacts the stopper pin 121, and the projection 124a of the stopper plate 124 contacts one end of the stopper plate 123. The angle of the fan of the stopper plate 124, the width of the stopper plate 123, the diameter of the stopper pin 121, each member so that the angle of the stopper plate 124 does not change when the other end of the plate 123 is in contact with the stopper pin 121. The position and so on are set.

Therefore, even when the electric coil 113 is energized to drive the electric motor 151 clockwise in the state of FIG. 4a, when the electric coil 113 is energized to drive the electric motor 151 counterclockwise in the state of FIG. 4d. However, the drive shafts of the electric motor 151 are positioned at the same angle. That is, in this example, the angle of the drive shaft of the electric motor 151 can be set to any one of three states by simple control of the electric motor 151 and the electric coil 113.

FIG. 5a is a cross-sectional view taken along line IIa-IIa of FIG. 1 in the state of FIG.
II of FIG. 1 in the state shown in FIG. 4b or 4c
The section taken along the line a-IIa is shown in FIG. 5b, and the section taken along the line IIa-IIa in FIG. 1 in the state of FIG. 4d is shown in FIG. 5c.

That is, as described above, through the permanent magnets 155 and 158a and 156 and 158b that are magnetically coupled to each other, the valve body is
Since 201 is connected to the drive shaft of the electric motor 151, if the electric motor is rotated clockwise by θ, the valve body 201
If the electric motor is rotated by θ and the electric motor is rotated by θ in the counterclockwise direction, the valve body 201 is also rotated by θ in the counterclockwise direction. That is, the position (angle) of the valve body 201 is set to one of three types of states.

In these three states, all are permanent magnets.
155 and 156 are present at positions facing the recess 164b of the rotation restriction ring 164. Therefore, even if the electric motor 151 is de-energized after each part is positioned at the predetermined position, the permanent magnets 155 and 156 are held at that position by the magnetic attraction force between the permanent magnets 155 and 156 and the rotation restricting ring 164. 201 is also held in that position.

FIG. 6a shows the structure of the piston mechanism 200 and the base valve mechanism 300 shown in FIG. 3 in detail. Also, a part of FIG. 6a is enlarged and shown in FIG. 6b, and different states of the cross section taken along the line VIII-VIII of FIG. 6a are shown in FIGS. 8a, 8b and 8c, respectively.
The different states of the cross section taken along the line IX-IX of FIG. 6a are shown in FIGS. 9a, 9b and 9c, and the different states of the cross section taken along the line XX of FIG. 6a are shown in FIGS. 10a, 10b and 10c. Shown in Figure, XI in Figure 6a
-See Fig. 11a, Fig. 11b and Fig.
Shown in Figure 11c.

First, the piston mechanism 200 will be described with reference to FIGS. 6a and 6b. A through hole 162b extending in the axial direction of the shock absorber is formed at the center of the rod 162, and the valve body 201 is rotatably arranged inside the through hole 162b. One end of the valve body 201 is a cylindrical portion 201b, and its inner space is a flow path. The rod 162 and the valve body 201 constitute a rotary valve. That is, the rod 162 functions as a valve seat.

In the portion of line VIII-VIII in Figure 6a, Figures 8a to 8c.
As shown in the figure, the flow path 16 is provided outside the valve body 201 in the rod 162.
2c and 162d are formed, and the valve body 201 has four orifices 2
31a, 231b, 232a and 232b are formed. Further, in the portion along line IX-IX in FIG. 6a, as shown in FIGS. 9a to 9c, flow paths 162e and 162f are formed outside the valve body 201 in the rod 162, and the valve body 201 has Four orifices 233a, 233b, 2
34a and 234b are formed. Further, in the portion of line XX in FIG. 6a, as shown in FIGS. 10a to 10c, flow paths 162g and 162h are formed outside the valve body 201 in the rod 162, and the valve body 201 has 5 Two orifices 235a, 235b, 236a, 236b
And 237 are formed. Further, in the portion along the line XI-XI in FIG. 6a, as shown in FIGS.
Flow paths 162i and 162j are formed outside the valve body 201 in 162.
Two orifices 238a and 238b are formed in the valve body 201.

Therefore, by rotating the valve body 201, each flow path formed in the rod 162, which is a valve seat, and the valve body 2 communicating with the flow path.
Correspondence with the orifice on 01 is switched. In this example, since the orifices have different characteristics, the piston mechanism 2 can be used depending on the position (rotation angle) of the rod 162.
The flow path resistance of 00 changes. That is, the movement characteristics of the piston are switched according to the position of the rod 162, and the damping force of the shock absorber is switched.

In this example, any one of the three types of damping force characteristics A, B and C shown in FIG. 7 can be selected. That is, when the characteristic A is selected, the stopper plate 124 may be positioned in the state shown in FIG. 4b or 4c. The state of the valve body 201 in this case is shown in FIGS. 5b, 8a, 9a, 10a, and 11a. When the characteristic B is selected, the stopper plate 124 may be positioned in the state shown in FIG. 4a. The state of the valve body 201 in that case is as shown in FIG.
This is shown in Figures 8b, 9b, 10b and 11b.

When the characteristic C is selected, the stopper plate 124
Should be positioned as shown in FIG. 4d. The state of the valve body 201 in this case is shown in FIGS. 5c, 8c, 9c, 10c, and 11c.

Referring again to FIG. 6a, this piston mechanism 200 has
In addition to the above, a check valve 221, a rear valve 222, a main valve 251, and the like are provided. The solid arrow in Fig. 6a indicates that the piston is to the left (extension direction) in Fig. 6a.
Shows the flow of hydraulic oil when moving to
Fig. 6 shows the flow of hydraulic oil when the piston moves to the right (contraction direction) in Fig. 6a.

The main valve 251 controls the flow of hydraulic oil when the piston moves to the left in FIG. 6a, and the check valve 221 and the back valve 222 flow the hydraulic oil when the piston moves to the right in FIG. 6a. To control.

The base valve mechanism 300 includes a check valve 301, a main valve 302, a valve seat 303, and so on. The check valve 301 controls the flow of hydraulic oil when the piston moves to the left in FIG. 6a, and the main valve 302 controls the flow of hydraulic oil when the piston moves to the right in FIG. 6a. .

In the above embodiment, the electric motor 151 and the valve body 201 mechanically separated by the cap 157 are magnetically coupled by the permanent magnets 154, 155 provided on the electric motor side and the permanent magnets 158a, 158b provided on the valve body side. Although the driving force is transmitted to the permanent magnets 158a and 158b by arranging an electric coil outside the cap 157 and changing the magnetic field generated by the electric coil, the permanent magnets 158a and 158b on the valve body side are directly driven. It may be configured. However, with such a configuration, the electric coil becomes large in size, so that the outer diameter of the portion for driving the valve body becomes large, and it is inevitable that the shock absorber becomes larger than in the above-described embodiment.

[Effects] As described above, according to the present invention, a sealing member such as an O-ring that comes into contact with the movable portion of the adjusting means such as a rotary valve or the drive shaft portion of the driving means is not required, so that the movable portion is generated. The frictional force is small and the moving part can be driven with a small force. Since the member for sealing is not in contact with the movable part, no wear occurs and fluid leakage does not occur. Further, the shape of the portion connecting the adjusting mechanism and the electric drive means is reduced, and the diameter of the shock absorber can be reduced. Moreover, since the rotation of the movable portion can be regulated at a specific position in a non-contact manner by a good magnetic force applied to the positioning means, no wear occurs and the movable portion is prevented from moving.
It is also possible to rotate 360 degrees.

[Brief description of drawings]

FIG. 1 is an enlarged view showing the actuator mechanism 100 of FIG. 3 in detail. 2a and 2b are cross-sectional views taken along the lines IIa-IIa and IIb-IIb in FIG. 1, respectively. FIG. 3 is a sectional view showing the entirety of one type of shock absorber for carrying out the present invention. Figures 4a, 4b, 4c and 4d show IV-IV of Figure 1.
It is sectional drawing which shows each different state seen from the line. 5a, 5b and 5c are cross-sectional views showing different states as seen from the line IIa-IIa in FIG. FIG. 6a is an enlarged view showing the piston mechanism and the base valve mechanism of FIG. 3 in detail, and FIG. 6b is an enlarged view showing a part of FIG. 6a. FIG. 7 is a graph showing damping force characteristics of the shock absorber of FIG. FIGS. 8a, 8b and 8c are sectional views showing different states as seen from the line VIII-VIII in FIG. 6a. 9a, 9b and 9c are cross-sectional views showing different states as seen from the line IX-IX in FIG. 6a. FIGS. 10a, 10b and 10c are sectional views showing different states as seen from the line XX of FIG. 6a. 11a, 11b and 11c are cross-sectional views showing different states as seen from the line XI-XI in FIG. 6a. 1: Rod, 2: Inner cylinder (casing) 3: Outer cylinder, 4: Lower seat 5: Guide member, 6: Seal 7: Nitrogen gas, 8: Spindle 9: Piston upper chamber, 10: Piston lower chamber 14: Hydraulic oil (Fluid) 110: Solenoid mechanism, 111: Plunger 120: Movable plate, 121: Stopper pin 122,126: Fixed stopper 123,124: Stopper plate 151: Electric motor (electric drive means) 155,156: Permanent magnet (Magnetic generation means) 157: Cap (Separator) 158a, 158b: Permanent magnet 162: Rod, 164: Rotation restriction ring 200: Piston mechanism (piston) 201: Valve body (movable part) 162 + 201: Rotary valve (adjustment mechanism) 221,301: Check valve 222: Rear valve 251,302: Main valve 231a to 238b: Orifice 300: Base valve mechanism

Claims (3)

[Claims] 1. A casing; a piston disposed in the casing to substantially separate the interior of the casing into at least two spaces; a fluid filled in the inner space of the casing; and a piston disposed in the inner space of the casing. An adjusting mechanism that adjusts the operating characteristics of the piston by including a permanent magnet on the axis of a movable portion that is movable; a drive source main body that is arranged at a position on an extension line of the rotation axis of the movable portion of the adjusting mechanism, and its drive shaft. An electric drive unit including a support member coupled to the at least one portion extending to an outer peripheral position of the movable portion, and a permanent magnet supported by the support member and arranged at a position facing the permanent magnet of the adjusting mechanism; The magnetic member is fixed to the outer side of the permanent magnet of the electric drive means, and includes a magnetic body in which unevenness is formed in accordance with a predetermined rotational position of the movable portion, and the movable portion is fixed in advance. A positioning means for restricting its rotation at a given rotational position; and the adjusting mechanism and the electric drive means are separated from each other, and the fluid filled in the inner space of the casing is sealed to remove the fluid from the fluid. A shock absorber with a built-in actuator, comprising: a separating means made of a non-magnetic material, which shields the electric driving means. 2. The adjusting mechanism is a rotary valve that adjusts a flow rate of a fluid passing between one space separated by the piston and the other space by rotation of the movable part, and the periphery of the movable part. The shock absorber with a built-in actuator according to claim (1), wherein at least one magnetic pole of the permanent magnet is disposed in the shock absorber. 3. The positioning means includes: an arm member having a central portion supported by a drive shaft of the electric drive means and rotatable about the shaft; one end thereof is fixed to the drive shaft of the electric drive means, A fan-shaped member in which projections are formed at both ends in the moving direction and the projections are arranged so as to surround one end of the arm member; a fixed restricting member that restricts a rotation range of the other end of the arm member; The actuator built-in device according to claim (1), further comprising: a protrusion drive means having a movable protrusion and driving the position of the protrusion to a position where it engages with the other end of the arm member and a position where it does not engage. Type shock absorber.