JPH109329A - Rotary damper using electrorheological fluid - Google Patents

Abstract

(57) [Summary] To rotate a rotating shaft in one direction and the other direction, control damping force characteristics independently of each other to simplify the device. SOLUTION: A rotating shaft 6 is rotatably provided while accommodating an electrorheological fluid 4 in a casing 1. Further, the first and second electrode tubes 26 and 3 are provided in the rotating tube 7 via a partition 22 or the like.
0 is provided, and each of the electrode tubes 26 and 30 is individually connected to the control unit 41. The inflow / outflow chamber B1 and the disc valve 1 are provided in a rotating cylinder 7 integrated with the rotating shaft 6.
8, distribution chamber C1, cylindrical passage 27, distribution chamber D, outflow / inflow chamber B
2 and a first flow path means comprising a check valve 35 and the like, an outflow / inflow chamber B2, a disc valve 2
0, distribution chamber C2, cylindrical passage 31, distribution chamber D, outflow / inflow chamber B
1 and a second flow path means comprising a check valve 39 and the like are provided, and the respective liquid chambers A1 and A2 communicate with each other via these flow path means.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary damper using an electrorheological fluid which is suitably used for, for example, damping a vibration acting on a vehicle or the like, and more particularly, to an electric damper which can appropriately adjust a damping force. The present invention relates to a rotary damper using a viscous fluid.

[0002]

2. Description of the Related Art Generally, vehicles and the like are equipped with a damper for damping external vibrations and shocks. As such a damper, for example, Japanese Unexamined Patent Publication No. 64-1
A damper described in Japanese Patent No. 2152 (hereinafter referred to as “prior art”) is known.

A conventional damper of this type is provided with a cylindrical casing provided with a fixed vane and containing an oil liquid therein, and rotatably provided in the casing, with both axial ends projecting outside the casing. And a first oil chamber and a second oil chamber are provided between the rotating shaft and the fixed vane. The first and second oil chambers are provided between the rotating shaft and the casing and provided on an outer peripheral side of the rotating shaft. The movable vane thus formed, a communication passage provided in the rotation shaft so as to communicate between the first and second oil chambers, and a communication passage provided in the middle of the communication passage and flowing through the communication passage. And a damping force generating mechanism for generating a damping force in the oil liquid.

When a conventional damper is mounted on, for example, a motorcycle or the like, a casing is fixedly provided on a vehicle body side, and a swing arm for swingably supporting the wheel side has a pivot shaft. By attaching the protruding end side, and when the swing arm swings up and down with respect to the vehicle body side due to vibration or the like during traveling, the rotation shaft is rotated with respect to the casing, so that the first and the second shafts are rotated. The oil liquid flows between the two oil chambers, and a predetermined damping force is generated by applying a throttle resistance to the oil liquid flowing in the communication passage at this time by a damping force generating mechanism.

Further, as another prior art, a rotary damper using an electrorheological fluid is disclosed in, for example, Japanese Utility Model Laid-Open No. 4-12700.
No. 5 publication.

In another conventional damper, an electrorheological fluid is contained in a casing, and a first vane and a second vane are disposed adjacent to each other between a fixed vane on the casing side and a movable vane on the rotating shaft side. An oil chamber is defined, and a throttle passage as a control gap is provided in the rotation shaft so as to communicate the liquid chambers with each other, and a pair of electrodes are arranged on the throttle passage side so as to face each other. And each of the electrodes is externally energized.

When the rotating shaft is rotated with respect to the casing, an electric field is applied between the electrodes to the electrorheological fluid flowing in the throttle passage to increase or decrease the viscosity of the electrorheological fluid. Thus, the flow resistance of the electrorheological fluid in the throttle passage is changed, so that the damping force can be easily controlled from the outside.

[0008]

By the way, in the above-mentioned prior art, a damping force generating mechanism is provided in the middle of a communication passage communicating between the first and second oil chambers. The damping force is only generated by the throttle resistance when the oil liquid flows through. Therefore, the damping force characteristics cannot be changed unless the disk valve or the like of the damping force generating mechanism is replaced or the area of the throttle passage is changed.
There is a problem that it is difficult to adjust the damping force by external remote control or the like.

On the other hand, in the case of another conventional technique, an electrorheological fluid is used in order to solve the above-mentioned problems of the conventional technique. However, such other conventional techniques have the following problems.

That is, when the rotating shaft rotates in one direction with respect to the casing and in the other direction, the electrorheological fluid merely flows through the same throttle passage in one direction or the other direction. For this reason, there is a problem that only the damping force having the same characteristic can be generated unless the electric field generated between the electrodes is changed according to the rotation direction of the rotation shaft.

In order to change the electric field between the electrodes in accordance with the direction of rotation of the rotating shaft, a sensor or the like for detecting the electric field is newly provided. Accordingly, it is necessary to change the electric field to be generated between the electrodes with high precision, which not only complicates and enlarges the configuration of the entire device, which leads to an increase in cost, but also provides stability and stability in variably controlling the damping force. There is a problem that it is difficult to improve reliability.

The present invention has been made in view of the above-mentioned problems of the prior art, and the present invention is applicable to a case in which a rotating shaft is rotated in one direction or another direction. Provided is a rotary damper that uses an electrorheological fluid that can independently control damping force characteristics without special detection of a direction and that can reliably improve control stability and reliability. It is intended to be.

[0013]

In order to solve the above-mentioned problems, a damper using an electrorheological fluid according to the present invention includes a tubular casing containing an electrorheological fluid therein and provided with a fixed vane. A rotating shaft provided to be relatively rotatable with respect to the casing, and a rotating shaft extending in the casing in the axial direction; and a rotating shaft provided between the rotating shaft and the casing and provided on the rotating shaft side; A movable vane defining first and second liquid chambers adjacent to each other between a fixed vane and the first liquid chamber when the rotation shaft is relatively rotated in one direction with respect to a casing; A first flow path means for flowing the electrorheological fluid from the second liquid chamber to the second liquid chamber, and preventing the flow in the opposite direction; The electrorheological fluid is transferred from the second liquid chamber to the first liquid chamber. A second flow path means for passing through the first flow path means and blocking the flow in the opposite direction; and a first flow path means provided in the middle of the first flow path means for energizing an electrorheological fluid flowing through the first flow path means. , And a second electrode unit provided in the middle of the second flow path means and supplying electricity to the electrorheological fluid flowing through the second flow path means.

With this configuration, when the rotating shaft is rotated in one direction with respect to the casing, the first shaft is rotated.
The electro-rheological fluid accommodated in the casing flows only in one direction from the first liquid chamber to the second liquid chamber by the flow path means. In the middle of the first channel means, the first
Since the first electrode section is provided, by applying a current to the first electrode section to generate an electric field in the first flow path means,
The viscosity of the electrorheological fluid flowing in the first flow path means can be increased, and the damping force can be adjusted by increasing or decreasing the viscosity of the electrorheological fluid.

Further, when the rotating shaft is rotated in the other direction with respect to the casing, the electrorheological fluid flows from the second liquid chamber to the first liquid chamber only in the other direction by the second flow path means. Become like Here, since the second electrode section is provided in the middle of the second flow path means similarly to the first flow path means, the second electrode section is energized and the second flow path is provided. By generating an electric field in the means, the viscosity of the electrorheological fluid flowing in the second flow path means can be increased, and the damping force is adjusted by increasing or decreasing the viscosity of the electrorheological fluid. be able to.

That is, the electric field generated in each of the throttle passages can be appropriately and separately adjusted by each of the electrode portions, so that the rotation shaft can be adjusted in one direction and in the other direction. The magnitude of the damping force generated by the damper can be controlled independently of each other.

[0017]

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

FIGS. 1 to 7 show an example in which a rotary damper using an electrorheological fluid according to an embodiment of the present invention is applied to a vehicle.

In FIG. 1, reference numeral 1 denotes a casing. The casing 1 is composed of a cylindrical casing body 2 having an open end 2A at one end and a closed end 2B at the other end, and a disc-shaped lid plate 3. And the casing body 2 has a closed end 2
A cylindrical bearing 2C protruding in the axial direction from the center of B,
An annular flange portion 2D protruding radially outward from the outer peripheral side of the open end portion 2A. A bearing portion 3A substantially similar to the bearing portion 2C is provided at the center of the cover plate 3, and the cover plate 3 is integrated with the flange portion 2D so as to close the casing body 2 in a sealed state. Installed.

Here, the casing 1 is integrally attached to, for example, the vehicle body side of the vehicle, and the casing 1 is filled (contained) with an electrorheological fluid 4. As shown in FIGS. 2 and 3, the casing 1 is provided with a plurality of fixed vanes 5, 5,. Each of the fixed vanes 5 extends in the shape of an elongated plate along the axial direction on the inner peripheral side of the casing 1, and projects radially inward from the inner peripheral surface of the casing 1. 7 is almost in sliding contact with the outer peripheral surface.

Reference numeral 6 denotes a rotating shaft provided rotatably with respect to the casing 1. The rotating shaft 6 extends inside the casing 1 along a central axis thereof, and both ends are provided at bearing portions 2 of the casing 1.
C and 3A are rotatably supported respectively. Then, as shown in FIG.
An annular stepped portion 6A is formed at one end in the axial direction.

A communication hole 6B is formed in a radially intermediate portion of the rotating shaft 4 so as to open into a temperature compensation chamber 46 to be described later.
Are formed. The rotating shaft 6 is connected to the bearing 2.
Each of the protruding ends protruding from C and 3A is integrally attached to, for example, an axle side (not shown), and when vibration or the like acts on the vehicle body, the casing 1 is shown by arrows R in FIGS.
1 and R2.

Reference numeral 7 denotes a rotating cylinder rotatably provided in the casing 1 so as to surround the outer peripheral side of the rotating shaft 6.
The rotary cylinder 7 extends cylindrically in the axial direction between the casing 1 and the rotary shaft 6 as shown in FIGS. 1 and 4, and has a plurality of outer circumferential sides as shown in FIGS. Are arranged at regular intervals along the circumferential direction. Each of the movable vanes 8 extends in the form of an elongated plate along the axial direction on the outer peripheral surface of the rotary cylinder 7 like the fixed vanes 5 and protrudes radially outward. It is almost in sliding contact with the inner peripheral surface of the casing body 2.

The movable vanes 8 define first and second liquid chambers A1 and A2, each having a sector shape in cross section with the fixed vanes 5, respectively. Room A1, A2
Are alternately arranged along the circumferential direction between the casing 1 and the rotating cylinder 7 so as to be adjacent to each other with the vanes 5 and 8 interposed therebetween. When each movable vane 8 is rotated relative to each fixed vane 5 about the rotary shaft 6 in the direction of arrow R1, the first and second liquid chambers A1 and A2 have reduced volumes, respectively. When the movable vanes 8 are relatively rotated in the direction of arrow R2, the first and second liquid chambers A1 and A2 have their respective volumes increased and decreased. .

Reference numerals 9 and 10 denote connecting cylinders provided on the outer peripheral side of the rotating shaft 6 at one end and the other end in the axial direction, respectively. One of the connecting cylinders 9 and 10 is FIG.
As shown in FIG. 5, a small-diameter cylindrical portion 9A in which the rotating shaft 6 is threadedly inserted on the inner peripheral side, and a cover plate 3 of the cylindrical portion 9A.
An annular plate portion 9B extending radially outward from one axial end side, and a large-diameter cylindrically extending axially extending from the outer peripheral side of the annular plate portion 9B to the lid plate 3 side. And a cylindrical portion with a stepped portion as a whole.

The connecting cylinder 9 has a cylindrical portion 9A and a rotating shaft 6
And a cylindrical portion 9A is provided with a pressing ring 40 (described later) provided on the stepped portion 6A side of the rotating shaft 6 and a rotating shaft 6 by a key 11 provided therebetween. And the nut 12 screwed to the outer peripheral side of the rotary shaft 6 is retained in the rotating shaft 6 so as not to be pulled out in the axial direction.

As shown in FIGS. 4 and 6, the connecting cylinder 10 is formed in substantially the same manner as the connecting cylinder 9 from a cylindrical portion 10A, an annular plate portion 10B, and a cylindrical portion 10C. The connecting cylinder 10 is held by a key 13 provided between the cylindrical portion 10A and the rotating shaft 6 in a state of being prevented from rotating with respect to the rotating shaft 6, and the annular plate portion 10B is fixed to the outer periphery of the rotating shaft 6. Pressing ring 36 and stopper plate 3 described below provided on the side
7 and the like, and is held in the axial direction with respect to the rotating shaft 6 in a state where it cannot be pulled out.

The connecting tubes 9 and 10 are connected to the cylindrical portion 9.
C and 10C are fitted in the rotating cylinder 7 in a liquid-tight manner, and integrally connect the rotating cylinder 7 to the rotating shaft 6. Here, the connecting cylinders 9 and 10 are provided between the lid plate 3 and the closed end 1B of the casing 1 on the outer peripheral side of the rotating cylinder 7 so as to form annular inflow / outflow chambers B.
1, B2. The cylindrical portions 9A and 10A of the connecting cylinders 9 and 10 are provided with annular valve seats 9A1 and 10A1 for check valves 39 and 35 described later, respectively, and the annular plate portions 9B and 10B are provided with annular valve seats 9A1 and 10A1, respectively. Annular valve seats 9B1 and 10B1 are provided for the respective disc valves 18 and 20 described later.

Reference numerals 14, 14,... Denote a plurality of communication holes which are located on the side of the first liquid chamber A1 and are provided in the rotating cylinder 7 and the connecting cylinder 9 so as to be circumferentially separated from each other. As shown in FIG. 2, the communication hole 14 is formed so as to penetrate the rotating cylinder 7 and the cylindrical portion 9C of the coupling cylinder 9 in the radial direction, and always connects the liquid chamber A1 to the inflow / outflow chamber B1. The communication holes 14 allow the electrorheological fluid 4 to flow from the liquid chamber A1 to the inflow / outflow chamber B1 when each of the movable vanes 8 is rotated in the direction of arrow R1. Is rotated in the direction of arrow R2, the electrorheological fluid 4 flows from the inflow / outflow chamber B1 to the liquid chamber A1.
It is allowed to flow in.

Reference numerals 15, 15,... Denote a plurality of other communication holes which are located on the side of the second liquid chamber A2 and are provided in the rotating cylinder 7 and the connecting cylinder 10 so as to be circumferentially separated from each other. As shown in FIG. 3, each communication hole 15 is formed so as to penetrate the rotating cylinder 7 and the cylindrical portion 10C of the coupling cylinder 10 in the radial direction, and always connects the second liquid chamber A2 to the inflow / outflow chamber B2. I have. When each movable vane 8 is rotated in the direction of arrow R1, the communication hole 15 allows the electrorheological fluid 4 to flow from the inflow / outflow chamber B2 to the second liquid chamber A.
2 and each movable vane 8 is rotated in the direction of arrow R2, the electrorheological fluid 4
From the liquid chamber A2 to the outflow / inflow chamber B2.

Are annular plate portions 9B of the connecting cylinder 9.
A first short axial flow passage, which is provided in the
Reference numerals 7, 17,... Denote second short-axis flow passages provided in the annular plate portion 10B of the connecting cylinder 10 in the circumferential direction so as to be spaced apart from each other. As shown in the figure, the annular plate portions 9B and 10B are formed so as to penetrate radially outside portions in the axial direction. Each of the flow passages 16 and 17
Connects the inflow / outflow chambers B1 and B2 to the later-described flow chambers C1 and C2 via the disc valves 18 and 20, respectively. Also,
Each of the flow passages 16, 17 has an opening 1 whose axially inner end is open to the valve seat 9 B 1, 10 B 1 of the connecting cylinder 9, 10.
6A and 17A.

Reference numeral 18 denotes a first disk valve as a damping force valve provided on the outer peripheral side of the cylindrical portion 9A of the connecting cylinder 9.
The disc valve 18 is mounted while being pressed against the valve seat 9B1 by a press ring 19 disposed between the disc valve 18 and a cylindrical holder 23 to be described later. 16A is opened and closed. An orifice (not shown) is formed in the valve seat 9B1.

Here, the hydraulic pressure in the outflow / inflow chamber B1 is equal to the flow chamber C
When the pressure becomes larger than the pressure on the first side and reaches the valve opening pressure of the disk valve 18, the disk valve 18 opens to open the opening 16A, and the electrorheological fluid 4 flows into the inflow / outflow chamber B1.
From the side to the flow chamber C1 through the respective flow passages 16, and the electrorheological fluid 4
, A constant flow resistance is given to the electrorheological fluid 4. Also, outflow / inflow chamber B1
When the internal fluid pressure becomes equal to or less than the valve opening pressure of the disc valve 18,
The disc valve 18 performs a valve closing operation so as to close the opening 16A, and prevents the electrorheological fluid 4 from flowing from the flow chamber C1 side to the inflow / outflow chamber B1 side through the respective flow passages 16.

Reference numeral 20 denotes a second disk valve as a damping force valve provided on the outer peripheral side of the cylindrical portion 10A of the connecting cylinder 10. The disk valve 20 is a presser provided between a cylindrical holder 24 described later. Attached to the valve seat 10B1 by the ring 21 in a state of being pressed, the opening 17A of each short axial flow passage 17 is opened and closed on the outer peripheral end side.

Here, the hydraulic pressure in the outflow / inflow chamber B2 is changed to the flow chamber C.
2 side, and when the pressure reaches the valve opening pressure of the disk valve 20, the disk valve 20 operates to open the opening 17A, and the electrorheological fluid 4 flows into the outflow / inflow chamber B2.
From the side to the flow chamber C2 through the respective flow passages 17, and the electrorheological fluid 4
, A constant flow resistance is given to the electrorheological fluid 4. Also, outflow / inflow room B2
When the internal fluid pressure becomes equal to or less than the valve opening pressure of the disc valve 20,
The disc valve 20 performs a valve closing operation so as to close the opening 17A, and prevents the electrorheological fluid 4 from flowing from the flow chamber C2 side to the inflow / outflow chamber B2 side via each short-axis flow passage 17.

Reference numeral 22 denotes an annular partition wall provided at an intermediate position in the axial direction on the inner peripheral side of the rotary cylinder 7. The partition wall 22 is formed as an annular flat plate, and has annular annular plates on both side surfaces along the circumferential direction. Mounting recesses 22A, 22A are formed. The partition 22 has its outer peripheral side fixed to the inner peripheral surface of the rotary cylinder 7 in a liquid-tight manner, and is provided between the cylindrical holders 23 and 24 and the electrode cylinders 26 and 3.
It is configured to hold 0. The partition wall 22 is provided between the rotating cylinder 7 and the electrode cylinders 26, 30 in a cylindrical flow chamber C1,
C2 is defined to prevent the flow of the electrorheological fluid 4 between the flow chambers C1 and C2.

Reference numerals 23 and 24 denote a pair of cylindrical holders provided on the connecting cylinders 9 and 10 side apart from each other in the axial direction of the rotating shaft 6, and each of the cylindrical holders 23 and 24 has an inner peripheral side. The connecting cylinders 9 and 10 are integrally attached to the cylindrical portions 9A and 10A of the connecting cylinders 9 and 10 in a screwed state. Each of the cylindrical holders 23 and 24 has an end face facing each other with the partition wall 22 interposed therebetween.
3A and 24A are formed.

25A and 25B are mounting grooves 2 of the partition wall 22.
Insulators provided in 2A, respectively, 25C and 25D indicate insulators provided in the mounting recessed grooves 23A and 24A of the cylindrical holders 23 and 24, respectively.
D is fitted at a position closer to the radial inside in each of the mounting concave grooves 22A, 23A, 24A. The cylindrical electrodes 26A, 30 of the electrode tubes 26, 30 are respectively provided in the insulators 25A, 25C and the insulators 25B, 25D.
A at both ends is fitted, whereby the cylindrical electrodes 26A,
30A is electrically insulated from the cylindrical electrodes 26B and 30B, respectively.

Reference numeral 26 denotes an electrode tube serving as a first electrode portion held between the partition wall 22 and the cylindrical holder 23. The electrode tube 26 is, as shown in FIGS. Small-diameter cylindrical electrodes 2 arranged concentrically on the outer peripheral side
6A and a large-diameter cylindrical electrode 26B.
6A and 26B have a minute gap in the radial direction.
Is formed. And the cylindrical electrode 2
6A is a mounting groove 22 of the partition wall 22 and the cylindrical holder 23 at both ends thereof via respective insulators 25A and 25C.
A, 23A are fitted in a liquid-tight manner, and both ends of the cylindrical electrode 26B are attached to the mounting grooves 22A, 23A, respectively.
A is directly fitted in A in a liquid-tight state.

Here, the cylindrical electrode 26B defines a cylindrical flow chamber C1 between the rotary cylinder 7 and the connecting cylinder 9 and the partition wall 22. The cylindrical electrode 26A, together with the cylindrical electrode 30A of the electrode tube 30, defines a cylindrical flow chamber D between the rotary shaft 6 and the connecting tubes 9 and 10. Restricted holes 28 and 29, which will be described later, are formed in the cylindrical electrodes 26A and 26B, respectively, and the cylindrical passage 27 communicates with the flow chambers C1 and D via the restricted holes 28 and 29, respectively.

The electrode tube 26 has a cylindrical electrode 26A connected to a control unit 41 and a power supply 43 via a lead wire 44 described later, and the cylindrical electrode 26B is connected to the ground. The cylindrical electrode 26A is energized from the control unit 41 side, and the cylindrical electrode 26A is turned on.
B, the inside of the cylindrical passage 27 and each of the throttle holes 28, 2.
9, an electric field is generated.

Are the cylindrical electrodes 2 of the electrode tube 26.
6A, a plurality of apertures spaced apart in the circumferential direction, 29,
Reference numerals 29,... Denote a plurality of apertures provided apart from each other in the circumferential direction of the cylindrical electrode 26B (only one is shown), and each of the apertures 28 is a cylindrical electrode. 26B
The cylindrical passage 27 is formed so as to radially penetrate an axially outer portion of the cylindrical passage 27 and communicates with the flow chamber C1. Each of the throttle holes 29 is formed to penetrate an inner portion in the axial direction of the cylindrical electrode 26A in the radial direction, and connects the cylindrical passage 27 to the flow chamber D.

Each of the throttle holes 28 and 29 constitutes a first throttle passage together with the cylindrical passage 27, and the electro-rheological fluid 4 flows from the flow chamber C1 side to the flow chamber D side. An electro-rheological fluid 4 flowing in the first throttle passage by an electric field generated in the electrode tube 26 while allowing the fluid to flow in the passage.
The aperture resistance is given to the aperture.

Reference numeral 30 denotes an electrode tube as a second electrode portion held between the partition wall 22 and the cylindrical holder 24. The electrode tube 30 is connected to the cylindrical electrode 30A as shown in FIGS. The first electrode tube 26 is formed substantially in the same manner as the first electrode tube 26 from the cylindrical electrode 30B, and a cylindrical passage 31 is formed between each of the cylindrical electrodes 30A and 30B. Both ends of the cylindrical electrode 30A are provided with insulating grooves 25A, 24A of the partition 22 and the cylindrical holder 24 via insulators 25B, 25D, respectively.
The two ends of the cylindrical electrode 30B are directly fitted in the mounting grooves 22A and 24A in a liquid-tight manner.

Here, the cylindrical electrode 30B is connected to the connecting cylinder 10
A cylindrical flow chamber C2 is defined between the rotary cylinder 7 and the partition 22 via the partition wall 22. Then, the cylindrical electrode 30
A and 30B are formed with throttle holes 32 and 33, respectively, which will be described later. The cylindrical passage 31 communicates with the flow chambers C2 and D through the throttle holes 32 and 33, respectively.

The electrode tube 30 has a cylindrical electrode 30A connected to a control unit 41 and a power supply 43 via a lead wire 45 described later, and a cylindrical electrode 30B connected to the ground. Then, the cylindrical electrode 30A is energized from the control unit 41 side, and the cylindrical electrode 30A is turned on.
B, the inside of the cylindrical passage 31 and each of the throttle holes 32, 3
3, an electric field is generated.

Are cylindrical electrodes 3 of the electrode tube 30.
A plurality of throttle holes 33, 33,
Reference numerals 33,... Denote a plurality of apertures provided apart from each other in the circumferential direction of the electrode tube 30A (only one of them is shown). The cylindrical passage 31 is formed so as to radially penetrate the outside portion in the axial direction, and communicates the cylindrical passage 31 with the flow chamber C2. Each of the throttle holes 33 is formed to penetrate a radially inner portion of the cylindrical electrode 30A in the axial direction, and connects the cylindrical passage 31 to the flow chamber D.

Each of the throttle holes 32 and 33 constitutes a second throttle passage together with the cylindrical passage 31, and the electro-rheological fluid 4 flows from the flow chamber C2 side to the flow chamber D side. The electro-rheological fluid 4 flowing in the second throttle passage is allowed by the electric field generated in the electrode tube 30 while allowing the fluid to flow in the passage.
The aperture resistance is given to the aperture.

Are cylindrical portions 10 of the connecting cylinder 10.
1A shows a first long-axis flow passage provided at a distance in the circumferential direction, and each of the long-axis flow passages 34 is formed through the cylindrical portion 10A in the axial direction as shown in FIGS. , Outflow / incoming room B
2 is communicated with the distribution room D. In addition, each long axial flow passage 3
4 is a valve seat portion 10A of the connecting cylinder 10 having an axially outer end portion.
The opening 34A is an opening 34A.

Reference numeral 35 denotes an annular check valve which is located on the connecting cylinder 10 side and is provided on the outer peripheral side of the rotating shaft 6. The check valve 35 is a pressing ring 36 screwed on the outer peripheral side of the rotating shaft 6. Thus, it is mounted in a state of being pressed against the valve seat 10A1 of the connecting cylinder 10. The check valve 35 is provided at its outer peripheral end side with the opening 3 of each long axial flow passage 34.
4A is opened and closed.

Here, the hydraulic pressure in the distribution chamber D is changed to the outflow / inflow chamber B2.
When it becomes larger, the check valve 35 opens to open the opening 34A, and the electrorheological fluid 4 flows from the flow chamber D side to the inflow / outflow chamber B2 side through the respective long axial flow passages 34. To allow it to flow. When the hydraulic pressure in the inflow / outflow chamber B2 becomes higher than that in the flow chamber D, the check valve 35 operates to close the opening 34A, and the electrorheological fluid 4 flows from the inflow / outflow chamber B2 to each of the long axial flow passages. It is configured to block the flow to the distribution chamber D side through the flow path 34.

The check valve 35 is connected to each communication hole 14, the inflow / outflow chamber B1, each short axial flow passage 16, the disc valve 18, the flow chamber C1, the first throttle passage (the cylindrical passage 27,
Each of the throttle holes 28 and 29), the flow chamber D, the inflow / outflow chamber B2, each of the long axial flow paths 34, and each of the communication holes 15 constitute a first flow path means. This is to allow the electrorheological fluid 4 to flow from the first liquid chamber A1 to the second liquid chamber A2 via the check valve 35, and to prevent reverse flow.

Reference numeral 37 denotes a stopper plate provided on the outer peripheral side of the rotary shaft 6 in the inflow / outflow chamber B2. The stopper plate 37 has an inner peripheral side on the outer peripheral side of the rotary shaft 6 as shown in FIGS. A threaded annular portion 37A, and a tubular portion 3 extending in a cylindrical shape in the axial direction from the annular portion 37A to the connecting cylinder 10 side.
7B, a plurality of communication holes 37C, 37C,... Are formed in the cylindrical portion 37B along the circumferential direction. The stopper plate 37 abuts the press ring 36 on the inner surface of the annular portion 37A so as to loosen the press ring 36 and to fix the distal end surface of the cylindrical portion 37B to the axially outer end surface of the annular plate portion 10B. , The connection cylinder 10 is prevented from coming off in the axial direction of the rotating shaft 6.

Reference numerals 38, 38, ... denote second long axial flow passages provided in the cylindrical portion 9A of the connecting cylinder 9 so as to be spaced apart in the circumferential direction.
Each of the long axial flow passages 38 is formed through the cylindrical portion 9A in the axial direction as shown in FIGS. 4 and 5, and connects the inflow / outflow chamber B1 to the flow chamber D. Each of the long axial flow passages 38 has an opening 38A whose outer end in the axial direction is open to the valve seat 9A1 of the connecting cylinder 9.

Reference numeral 39 denotes an annular check valve provided on the connecting cylinder 9 side and provided on the outer peripheral side of the rotating shaft 6. The check valve 39 is a presser fitted to the step 6 A of the rotating shaft 6. The ring 40 is attached while being pressed against the valve seat 9A1 of the connecting cylinder 9. The check valve 39 is provided at its outer peripheral end side with the opening 3 of each long axial flow passage 38.
8A is opened and closed.

Here, the hydraulic pressure in the distribution chamber D is changed to the outflow / inflow chamber B1.
When it is larger than the side, the check valve 39 opens to open the opening 38A, and the electrorheological fluid 4 flows from the flow chamber D side to the inflow / outflow chamber B1 side through the respective long axial flow passages 38. It is allowed to flow. Also,
When the hydraulic pressure in the outflow / inflow chamber B1 becomes larger than that in the flow chamber D,
The check valve 39 operates so as to close the opening 38A, and is configured to prevent the electrorheological fluid 4 from flowing from the inflow / outflow chamber B1 side to the flow chamber D side through the respective long axis flow passages 38.

The check valve 39 is connected to each communication hole 15, the inflow / outflow chamber B2, the disc valve 20, each short axial flow passage 17, the flow chamber C2, the second throttle passage (the cylindrical passage 31,
Each of the throttle holes 32, 33), the flow chamber D, the inflow / outflow chamber B1, the respective long axial flow passages 38, and the respective communication holes 14 constitute second flow passage means. The check valve 39 allows the electrorheological fluid 4 to flow from the second liquid chamber A2 to the first liquid chamber A1,
It blocks the reverse flow.

Reference numeral 41 denotes a control unit. The control unit 41 is connected to a power supply 43 via a lead wire 42 and is connected to the cylindrical electrodes 26A, 30A of the electrode tubes 26, 30 via lead wires 44, 45 and the like. Each is connected individually. And the control unit 41
Can independently and appropriately adjust the applied voltage output from the power supply 43 to each of the cylindrical electrodes 26A and 30A according to the vibration state of the damper.

Reference numeral 46 denotes a temperature compensating chamber formed so as to extend in a cylindrical shape from the one end in the axial direction to an intermediate portion in the rotating shaft 6, and a free piston 46A is provided in the temperature compensating chamber 46.
Is slidably provided, and the inside of the temperature compensation chamber 46 communicates with a gas chamber 46B such as air whose both ends are sealed via the free piston 46A, and one end communicates with the inside of the circulation chamber D via the communication hole 6B. A liquid chamber 46 into which the electrorheological fluid 4 can flow.
And C. When the volume of the electrorheological fluid 4 changes due to a temperature change or the like, the temperature compensating chamber 46 slides and moves the free piston 46A to displace the gas chamber 46.
By expanding and contracting C, the volume change of the electrorheological fluid 4 is compensated.

The rotary damper according to the present embodiment has the above-described configuration, and its operation will be described below.

First, external vibrations act on the rotary damper, and as shown in FIG.
, The liquid chambers A1,.
Since the volume of A2 decreases and increases, the electrorheological fluid 4 in each liquid chamber A1 flows into the inflow / outflow chamber B1 through each communication hole 14.

Here, since the disc valve 18 and the check valve 39 are provided in each of the short-axis flow passages 16 and each of the long-axis flow passages 38, the electrorheological fluid 4 flowing into the inflow / outflow chamber B1 is supplied to each While passing through the disc valve 18 from the long axial flow passage 38 and flowing through the flow chamber C1,
After flowing through the throttle passage formed by the throttle holes 28 and 29 and the cylindrical passage 27, the gas flows through the flow chamber D.
The disc valve 20 and the check valve 35 are provided in each of the short axial flow passages 17 and the long axial flow passages 34, respectively.
Is provided, the electrorheological fluid 4 flowing through the flow chamber D flows out of each short-axis flow passage 17 through the check valve 35 into the flow-in / flow-out chamber B2, and each communication hole 1
5 through each of the liquid chambers A2.

As described above, when the rotating shaft 6 is relatively rotated in the direction of arrow R1, the electrorheological fluid 4 is supplied to each communication hole 1
4. Outflow / inflow chamber B1, each short axial flow path 16, disc valve 18, flow chamber C1, first throttle path (cylindrical path 27, each throttle hole 28, 29), flow chamber D, each long axial flow path 34. , The check valve 35, the inflow / outflow chamber B2, and the communication holes 15, the first flow path means is moved from each liquid chamber A1 to each liquid chamber A2.
And the flow in the opposite direction can be prevented.

Also, as shown in FIG.
When they are relatively rotated in two directions, contrary to the above-described case, the electrorheological fluid 4 is supplied to each communication hole 15 and the inflow / outflow chamber B2.
, Disk valve 20, each short axial flow passage 17, flow chamber C2
, A second throttle passage (cylindrical passage 31, each throttle hole 32, 3)
3), flow chamber D, each long axial flow passage 38, check valve 3
9. In the second flow path means comprising the inflow / outflow chamber B1 and each communication hole 14, the liquid can be circulated from each liquid chamber A2 to each liquid chamber A1, and the flow in the opposite direction can be prevented. .

That is, in the damper according to the present embodiment, when the rotating shaft 6 is relatively rotated in the direction of arrow R 1,
The electrorheological fluid 4 can be separately circulated in the first and second throttle passages when the relative rotation is performed in two directions.

The cylindrical electrodes 26A of the electrode cylinders 26 are connected to the control unit 4 via lead wires 44, respectively.
1, the voltage applied from the control unit 41 is output to the cylindrical electrode 26A to output the applied voltage from the control unit 41 to the cylindrical electrode 26A, for example, when the rotary shaft 6 is relatively rotated in the direction of arrow R1.
A, by generating an electric field between A and 26B,
Throttle resistance can be given to the electrorheological fluid 4 flowing through the throttle passage of this type, and the damping force can be increased by increasing the throttle resistance of the electrorheological fluid 8.
In addition, when the electrorheological fluid 4 flows from the inflow / outflow chamber B1 through the short-axis flow passages 16 through the flow chamber C, a throttle resistance can be given in advance by the disk valve 18, thereby providing a damping force. Can be further increased.

When the rotating shaft 6 is relatively rotated in the direction indicated by the arrow R2, the voltage applied from the control unit 41 is output to the cylindrical electrode 30A of the electrode tube 30 and the cylindrical electrode 3 is turned on.
By generating an electric field between 0A and 30B, throttle resistance can be given to the electrorheological fluid 4 flowing through the second throttle passage, and the throttle resistance of the electrorheological fluid 4 is increased as described above. As in the case, the damping force can be increased. In addition, the flow of the electrorheological fluid 4 from the inflow / outflow chamber B2 to the flow chamber C
Since the throttle resistance can be given in advance by the disk valve 20 when flowing through the inside 2, the damping force can be further increased. At the time of such rotation, a slight fluid leak occurs between the casing 1 and the movable vane 8 and the like.

Thus, in this embodiment, the electrode cylinders 26, 3
Since the cylindrical electrodes 26A, 30A of the “0” are individually connected to the control unit 41 via the lead wires 44, 45 and the like, respectively,
By appropriately adjusting the applied voltages output to A and 30A, different throttle resistances can be given to the electrorheological fluid 4 flowing through the first and second throttle passages, Thus, the damping force generated by the damper can be independently controlled when the rotating shaft 6 rotates in the direction of arrow R1 and when the rotating shaft 6 rotates in the direction of arrow R2. Can be changed to desired sizes according to the vibration state acting on the damper.

Here, as shown in FIG. 7, an experiment was conducted to investigate the damping force characteristics of the damper when the rotating shaft 6 was rotated relative to the arrows R1 and R2, respectively. The horizontal axis represents the angular velocity (corresponding to the magnitude of the vibration acting on the damper), and the vertical axis represents the damping torque (corresponding to the damping force generated by the damper).

Here, a characteristic line E shown by a dotted line in FIG.
A case where the rotating shaft 6 is rotated in the direction of arrow R1 in a state where no voltage is applied to the electrode tube 26 is shown, and a characteristic line F shown by a solid line
Indicates a case where the rotating shaft 6 is rotated in the direction of arrow R1 while a predetermined voltage is applied to the electrode tube 26. A characteristic line G indicated by a two-dot chain line indicates a case where the rotating shaft 6 is rotated in the direction of arrow R2 without applying a voltage to the electrode tube 26, and a characteristic line H indicated by a one-dot chain line is The case where the rotating shaft 6 is rotated in the direction of arrow R2 in the state where a constant voltage is applied to the rotating shaft 6 is shown.

At low angular velocities below the inflection point I in FIG. 7, the orifices and casing 1 provided in the valve seat 9B1 and the movable vane 8 are provided with the disk valves 18 and 20 not opened. A damping force is generated due to a leak during the period. Then, when the angular velocity becomes equal to or higher than the inflection point I, the disk valves 18 and 20 are opened to generate a damping force.

As is clear from these characteristic lines E to H, as the angular velocity increases, the damping torque can be increased, and the characteristic lines E and F in which the rotating shaft 6 is rotated in the direction of arrow R1. And the characteristic line G, which is rotated in the direction of arrow R2,
The damping force characteristics different from those in the case of H can be obtained, and the damping force torque generated by the damper as shown by the characteristic lines F and H can be increased by applying voltages to the electrode tubes 26 and 30, respectively. it can.

Further, by separately adjusting the voltages applied to the electrode cylinders 26 and 30, the rotating shaft 6
The damping force characteristics when rotating in the 1 and R2 directions can be independently changed, and the damping force can be increased as the voltage value is increased.

Further, even when a voltage of the same value is applied to the electrode cylinders 26 and 30, the radial dimensions of the throttle holes 28, 29, 32 and 33 or the cylindrical passages 27 and 31 are changed to each other, so that The flow resistance of the fluid 4 can be set to different values from each other, and the damping force characteristics can be changed according to the rotation direction of the rotating shaft 6.

Therefore, in the present embodiment, the applied voltage from the control unit 41 is separately output to the electrode cylinders 26 and 30 separately in advance in accordance with the vibration acting on the vehicle.
When the rotating shaft 6 is rotated in the direction of arrow R1 or in the direction of arrow R2, the desired damping force characteristics for the vibration can be generated independently of each other. As described in the art, a sensor or the like for detecting the rotation direction of the rotation shaft 6 can be eliminated, thereby simplifying the entire structure and downsizing.

By appropriately changing the voltage applied from the control unit 41 to the electrode cylinders 26 and 30, the turning shaft 6 is turned in the direction of the arrow R 1 in accordance with the road surface condition during traveling. And when it is rotated in the direction of arrow R2, the damping force characteristics generated by the damper can be independently stabilized and adjusted independently, and the stability and reliability when the damping force is adjusted by the damper can be ensured. Can be improved.

In the above embodiment, the check valves 35 and 39 are provided on the long axial flow paths 34 and 38, respectively, and the disc valves 18 and 20 are provided on the short axial flow paths 16 and 17. However, the present invention is not limited to this. For example, the disc valves 18 and 20 may be omitted, and the flow direction of the electrorheological fluid 4 may be determined by the check valves 35 and 39.

In the above embodiment, the damper is applied to a motorcycle or the like. However, the present invention is not limited to this, and may be applied to a vehicle such as a four-wheeled vehicle. It may be applied to devices and precision equipment.

[0079]

As described in detail above, according to the present invention, when the rotating shaft is relatively rotated in one direction with respect to the casing, the first passage means is used when the rotating shaft rotates relative to the casing in one direction. The electro-rheological fluid flows from the first liquid chamber toward the second liquid chamber, and the second flow path means causes the second flow path to rotate when the rotation shaft rotates relative to the casing in the other direction. The electrorheological fluid is caused to flow from the liquid chamber toward the first liquid chamber, and an electric current flowing in the first and second flow path means is provided in the middle of the first and second flow path means. Since the first and second electrode portions for energizing the viscous fluid are provided, the electric field generated in each of the flow path means is separately adjusted by each of the electrode portions, so that the rotating shaft is rotated in one direction. The damping force characteristics of the damper when moving it and turning it in the other direction It can be controlled independently.

Therefore, when vibration or the like is applied from the outside, the desired damping force characteristics for the vibration are independent of each other when the rotating shaft rotates in one direction and when the rotating shaft rotates in the other direction. As described in other related arts, it is possible to eliminate the need for a sensor for detecting the rotation direction of the rotation shaft, thereby simplifying the entire structure, reducing the overall size, etc. Can be achieved.

Also, by appropriately changing the voltage applied to the first and second electrode portions, the rotation shaft is rotated in one direction in accordance with the vibration acting on the damper, and in the other direction. The damping force characteristics of the damper can be adjusted independently of each other when the damper is rotated, and the stability and reliability when adjusting the damping force can be reliably improved.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a rotary damper according to an embodiment of the present invention, taken along a line II in FIG.

FIG. 2 is a sectional view taken in the direction of arrows II-II in FIG.

FIG. 3 is a sectional view taken in the direction of arrows III-III in FIG.

FIG. 4 is an enlarged sectional view of a main part in FIG. 1, showing an electrode tube, a disk valve, and the like.

FIG. 5 is an enlarged cross-sectional view of a main part showing a first cylindrical electrode side in FIG. 4;

FIG. 6 is an enlarged cross-sectional view of a main part showing a second cylindrical electrode side in FIG. 4;

FIG. 7 is a characteristic diagram of damping force showing a relationship between an angular velocity of a rotating shaft and a damping force torque.

[Explanation of symbols]

 Reference Signs List 1 casing 4 electrorheological fluid 5 fixed vane 6 rotating shaft 8 movable vane 14, 15 communication hole 16, 17 short axial flow passage 18 disk valve 20 disk valve 26 first electrode tube (first electrode part) 27 first Cylindrical passage 28, 29 throttle hole 30 second electrode tube (second electrode portion) 31 second cylindrical passage 32, 33 throttle hole 34 long axial flow passage 35 check valve (first flow passage means) 38 Long axis flow passage 39 Check valve (second flow path means) A1 first liquid chamber A2 second liquid chamber B1 outflow / inflow chamber B2 outflow / inflow chamber C1 flow chamber (first flow path means) C2 flow chamber (second flow path means) 2 Flow means) D Flow chamber

Claims (1)

[Claims] 1. A cylindrical casing containing an electrorheological fluid therein and provided with fixed vanes, and a rotating shaft provided rotatably relative to the casing and extending in the casing in the axial direction. A movable liquid chamber disposed between the rotating shaft and the casing and provided on the rotating shaft side and defining first and second liquid chambers adjacent to each other with the fixed vane; When the rotation shaft rotates relative to the casing in one direction with respect to the vane, the electrorheological fluid flows from the first liquid chamber toward the second liquid chamber, and prevents the flow in the opposite direction. A first flow path means, and a first liquid passage from the second liquid chamber when the rotation shaft rotates relative to the casing in another direction;
A second flow path means for circulating the electrorheological fluid toward the liquid chamber of the first flow path means, and a second flow path means for preventing flow in the opposite direction; A first electrode section for supplying electricity to the electrorheological fluid flowing through the second flow path means, and a second electrode for supplying electricity to the electrorheological fluid flowing in the second flow path means and provided in the second flow path means And a rotary damper using an electrorheological fluid.