JP3053156B2 - Fluid pressure damper - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary type fluid pressure damper, which is used for an opening / closing portion of a lid or a toilet seat of various devices.

[0002]

2. Description of the Related Art As described in the Mechanical Engineering Handbook, a rotary hydraulic damper has a structure in which a partition wall is formed on an inner wall of a cylinder, and a shaft provided with wings is rotated in the cylinder. ,
When the blade is rotated with oil filled in the cylinder, hydraulic pressure is generated between the blade and the partition, and oil leaks from gaps between the blade and the inner wall of the cylinder and between the partition and the shaft. Braking, that is, a damper effect is obtained. In this structure, the same damper action is performed in both forward and reverse rotations of the shaft.

However, when the lid is opened and closed, there is a case where the door is closed gently via a damper when closed by its own weight, and a damper action is not required when the lid is opened. There is a damper action mainly in one direction of the shaft rotation. There is also a configuration in which the damper effect is weakened in the rotation direction. Examples thereof are the structures described in JP-A-4-282036 and JP-A-3-267027.

The former has a structure as shown in FIG. 12 (a), in which a partition 11 is provided on the inner wall of a casing 1, and a basic structure in which a shaft 2 with a rotary wing 21 in the casing 1 rotates. Is the same as that described above, except that the length of the rotary blade 21 is short, and
2 and includes a movable valve 9 </ b> A disposed between the rotor 21 and the inner wall of the casing 1. This movable valve 9A has a substantially U-shaped cross section, and one of the projecting portions on both sides is a closed wall 9A.
1 and the other have a notch 92 corresponding to the fluid passage 22, and the interval between the closing wall 91 and the notch 92 is formed wider than the width of the rotary blade 21. In the figure, above the horizontal center line is a state where the rotor 21 is rotating in the direction of the arrow and acting as a damper. At this time, the fluid passage 2 of the rotor 21
Reference numeral 2 is closed by a closing wall 91 of the movable valve 9A. On the other hand, below the horizontal center line, the rotary wings 21 rotate in the opposite direction to act as a damper, and the oil contained in the casing 1 flows from the fluid passage 22 through the notch 92 of the movable valve 9A. The leakage increases. To increase the damper action,
The dynamic viscosity of the fluid to be filled, it is necessary to use a high viscosity above 10,000 cSt (cm <br/> Stokes).

The latter has a structure as shown in FIG. The movable valve 9B has one end supported by the shaft 2 and
And a stopper 23 protruding from the shaft 2 for restricting one rotation of the movable valve 9B. In the figure, the movable valve 9B is located above the horizontal center line.
Is rotating in the direction of the arrow, and is acting as a damper in a state where the swing is restricted by the stopper 23. On the other hand, below the horizontal center line, the movable valve 9B rotates in the opposite direction. At this time, the gap between the movable valve 9B and the inner wall of the casing 1 is increased by the hydraulic pressure, and the damper action is reduced.

[0006]

SUMMARY OF THE INVENTION The above-mentioned conventional improvement is achieved by using a devised movable valve 9A or movable valve 9B.
This is to obtain the damper function exclusively in one direction.
The former has a feature that when the movable valve 9A is incorporated, the shaft rotation direction for obtaining the damper function can be changed only by changing its direction. However, the outer and inner peripheral surfaces of the movable valve 9A are in sliding contact with each other. , Closing wall 9 of movable valve 9A
Since the gap at the time of contact between the rotor 1 and the rotor 21 directly affects the damper performance, the damper characteristics tend to vary due to manufacturing dimensional errors and wear between the members, and there is a problem in quality stability. In addition, since a high-viscosity fluid is used, there is a problem that the amount of change in viscosity is large due to a change in environmental temperature, and the change in damper characteristics is remarkable. Similarly, the latter also has a movable valve 9B
Since the structure rotates, high precision dimensional accuracy is required, and another shaft member must be prepared for changing the damper action direction, which cannot be easily performed. In some cases, the performance or damping force of the damper may be adjusted as required, and there is a demand for achieving this with a simple structure.

SUMMARY OF THE INVENTION An object of the present invention is to provide a fluid pressure damper which can easily change the rotation direction of the shaft for obtaining the damper function, has few sliding contact points, and has a simple structure.
The other purpose is that, with the conventional structure, the accuracy of parts, assembly accuracy,
No consideration was given to variations and changes in damper performance or braking force due to oil viscosity changes due to wear between parts and temperature changes, etc., but adjustment means were provided with the simplest possible configuration to adjust to the desired damper performance. To be able to do it. Still another object is to enable a mechanism for stopping rotation of a shaft at a predetermined angular position with a smaller number of parts.

[0008]

An object of the present invention is to provide a cylindrical chamber 14 of a casing 1 having a partition wall 11 protruding from an inner wall, which is a main part of the present invention. In the fluid pressure damper filled with the viscous fluid, a fluid passage 22 is provided in the rotating blade 21, and a sliding contact portion 33 that covers a tip end surface of the rotating blade 21 and contacts an inner wall of the casing, and one of the fluid passage 22. An elastic valve portion 31 covering the side opening, and being hooked on the other side of the fluid passage 22;
Section 7 in which the short piece-shaped locking portion 32 is integrally formed.
Has a seal member 3 of the shaped sealing member 3 is the locking portion 3
2 and is rotatable integrally with the rotating blade 21 while being hooked through the elastic blade portion 3.
This is achieved by the configuration in which 1 is rotated only in one direction of the shaft 2 by receiving the fluid pressure of the viscous fluid entering through the other port of the fluid passage 22 and swings to open one port of the fluid passage 22. .

[0009] In the above-mentioned main part configuration, the sealing member 3 is
The sliding contact portion 33 that covers the tip end surface of the rotating blade 21 and contacts the inner wall of the casing, the elastic valve portion 31 that covers one side opening of the fluid passage 22, and the sliding contact portion 38 that covers one end surface of the rotating blade 21 are integrally formed. Preferably. Also, as in claim 2
The rotating blade 21 has a vertical hole 22a communicating with the fluid passage 22 from the tip end face of the rotating blade 21 toward the axial direction along with the fluid passage 22, while the sealing member 3 covers the tip end face of the rotating blade 21 and covers the inner wall of the casing. A sliding contact portion 33 that contacts
The fluid passage 22 is inserted into the vertical hole 22a and is inserted into the vertical hole 22a.
It is preferably formed in a substantially T-shaped cross-section integrally having an elastic valve portion 31 covering the same. In this case, the seal member 3 has a sliding contact piece 39 arranged along one end face of the rotary wing 21, and is urged by the sliding contact piece 39 in a direction protruding from the tip end face of the rotary wing 21. It is more preferable to do so.

In the above-mentioned main part configuration, the casing 1 has a substantially cup-like shape, has a closing lid 5 to which a bolt 62 is fastened on the opening side of the cup-like shape. An elastic member 81 is interposed between the cylindrical members 14 of the casing 1 according to the tightening force of the bolts 62.
It is preferable to provide a braking force adjusting mechanism 8 that can change the axial position of the shaft 2 and the rotary wing 21 with respect to. In the main part configuration, the locking groove 16 provided on the inner wall of the casing 1 and the claw portion 72 which is mounted on the outer periphery of the shaft 2 and slidably contacts the inner wall and removably engages with the locking groove 16. It is more preferable to provide the rotation stopping mechanism 7 including the spring member 71 that is provided.

In the present invention, the viscous fluid includes oils of various viscosities, liquids such as water, and gases such as air. The fluid passage provided in the rotor is formed in a round or elliptical cross section, or a cutout communicating with the outer diameter of the rotor as in FIG. 9A. In this case, when the rotor is made of resin, it can be formed simultaneously with molding by a mold configuration.
The seal member covering a part of the rotor is rubber, metal,
It is molded using a material exhibiting elasticity such as resin, and is particularly preferably a molded product of nitrile rubber or a copper alloy plate. When the viscous fluid is a gas, it is preferable to apply a synthetic oil for lubrication between the sealing member and the inner cylinder wall and for improving the sealing property. The spring member of the rotation stopping mechanism,
One that cuts grooves from the outer diameter of a resin or metal disk, or that forms a thin-walled part and forms a spring body,
It is formed of a metal wire spring. In addition, a shaft or the like having a rotor or the like is assembled to the casing, and an outlet for injecting a viscous fluid or discharging an excess fluid can be provided at the shaft center portion or the outer diameter portion of the casing. Sealed. In addition, the number of casing partition walls and the number of rotors
If it is one or more, it functions and is determined by the required rotation angle of the shaft and the performance of the damper. When the shaft rotation angle is about 100 degrees, two partition walls and two rotor blades are usually provided.
Hereinafter, a hydraulic damper of the present invention will be described with reference to an embodiment shown in the drawings.

[0012]

1 (a) and 1 (b) are longitudinal sectional views of a hydraulic damper according to a first embodiment of the present invention, FIG. 2 is a transverse sectional view of the hydraulic damper, and FIG. FIG. 4 (a),
(B), (c) is an enlarged view which shows three examples of the principal part. In the drawings, the same members or parts as those in the related art are denoted by the same reference numerals.

The hydraulic damper shown in each figure has a partition wall 1 on the inner wall.
1, a shaft 2 with a rotary blade 21 incorporated in the casing 1, a seal member 3 fixed to the tip end surface of the rotary blade 21, and a sealing for preventing fluid leakage from the opening of the casing 1 4 and a closing lid 5 attached together.

The casing 1 has a substantially cup shape.
A viscous fluid injection port 12 is provided at a portion corresponding to the bottom, and the inner side also serves as the bearing section 13, and the outer side is formed in a female screw and formed in a hole into which a sealing bolt 61 can be screwed. On the inner wall of the casing 1, two partition walls 11 are provided.
4 protrudes. The shaft 2 has a shaft hole 24 on a protruding portion side protruding from the casing 1, a portion that slides on the inner wall of the casing and arranges the sealing 4 in the circumferential groove, a portion including the pair of rotor blades 21 illustrated in FIG. 3, and The small diameter shaft part 25 supported by the bearing part 13 is integrally provided. The shaft hole 24 is fitted with a shaft such as a lid that requires a damper action.

The rotary wing 21 is provided with a fluid passage 22 having an elliptical cross section or an oval shape as shown in FIG.
A seal member 3 having an elastic valve portion 31 is provided on the distal end surface side. This seal member 3 has a substantially 7-shaped cross section having an elongated elastic valve portion 31 on one side. Sealing member 3
As shown in FIG. 4A, a short piece-shaped locking portion 32 is integrally provided on the side where the fluid passage 22 is opened, and the locking portion 32 is rotated on the tip end surface side of the rotary wing 21. The blade 21 is attached to the upper edge of one side of the blade 21 with its tip end surface covered with a sliding contact portion 33. The elastic valve portion 31 covers one opening of the fluid passage 22 so as to be openable and closable.

The measures for preventing the sealing member 3 from falling off are not limited to the locking portions 32, but the locking portions 32 are extended as shown in FIG.
A method of forming an opening portion 34 for releasing a groove, as shown in FIGS. 13B and 13C, providing a concave portion or an uneven portion on the tip end surface of the rotary blade 21 and a convex portion 35 or an uneven portion corresponding to the seal member 3 side. It is effective to provide an engaging projection 37 on the side of the seal member 3 and hook it on the edge of the hole of the fluid passage 22 as shown in FIG. It is possible.

The above-mentioned components are assembled by inserting the shaft 2 with the rotary wings 21 into the cylindrical chamber 14 of the casing 1 with the sealing 4 interposed therebetween, filling the injection port 12 with a viscous fluid, and then filling the shaft. 2 is fixed to a fixed position, the closing lid 5 is put on, and the bolts 61 are used to tighten the screw holes 15 provided on the end face of the opening flange of the casing 1 using a plurality of bolts 62. It is completed by being done.

[0018]

In the above-described fluid pressure damper, as shown in FIG. 1 (a) showing the operation of the damper, when the shaft 2 is rotated in the direction of the arrow, the fluid passage 22 is connected to the elastic valve of the seal member 3. It is always closed by the part 31. As a result, the viscous fluid moves exclusively through the fitting gap 16 between the partition 11 and the shaft 2, and operates with a braking force having a strength proportional thereto. Also,
FIG. 2B shows a state when the shaft 2 is reversed.
In the process of the reverse rotation, the viscous fluid enters the fluid passage 22 and presses the elastic valve portion 31 in the opening direction.
The fluid passage 22 is released. As a result, the viscous fluid passes through the partition 1
In addition to the fitting gap 16 between the shaft 1 and the shaft 2, the fluid passage 2
2 and can be operated with a weak braking force proportional thereto.

In the structure of the fluid pressure damper, since the seal member 3 is fixed to the tip end portion of the rotary blade 21, only the outer surface of the sliding contact portion 33 where the seal member 3 contacts the inner wall of the casing 1. It just wears. Therefore, it is only necessary to consider the thickness control of the sliding contact portion 33 and the wear of the outer surface thereof as quality control, and it is necessary to consider the fitting dimensional accuracy and wear of the contact portion between the seal member 3 and the rotary blade 21 as in the related art. There is no need to consider it, and accuracy is greatly reduced. Here, if the seal member 3 is made of a rubber material and is formed to be thicker than the gap between the rotary blade 21 and the inner wall of the casing 1, the seal member 3 comes into close contact with the inner wall, and the sealing property of the viscous fluid is improved. The elastic valve portion 31 covering the fluid passage 22 swings and deforms only when the fluid pressure from the fluid passage 22 is applied, and acts as a one-way valve that releases the fluid passage 22. Further, since the shape of the seal member 3 has a substantially 7-shaped cross section, the rotation direction in which the braking force is obtained can be changed by changing the mounting direction with respect to the rotary wing 21.

FIGS. 5 to 7 show three examples in which functions are added to the structure of the seal member 3. FIG. FIG. 5 (a),
(B) shows a second embodiment of the seal member 3, in which a sliding contact portion 38 is provided on the side of the casing 1 corresponding to the bottom of the cup shape separately from the sliding contact portion 33. That is, the second
The seal member 3 according to the embodiment includes a sliding contact portion 33 that covers the tip end surface of the rotary wing 21 and is in contact with the inner wall of the casing.
2 is a resin molded body integrally having an elastic valve portion 31 covering one side opening and a sliding contact portion 38 covering one end surface of the rotary blade 21. In this configuration, in addition to the above operation, the sliding contact portion 38 elastically contacts the bottom surface of the cup shape,
The sealing property of that portion is reliably obtained.

FIGS. 6A and 6B show a third example of the seal member 3.
An example is shown. The seal member 3 of the third embodiment is formed in a substantially T-shaped cross-section that integrally includes a sliding contact portion 33 that covers the tip end surface of the rotor blade 21 and contacts the inner wall of the casing and an elastic valve portion 31a. . The rotating blade 21 has a vertical hole 22a communicating with the fluid passage 22 from the tip end face of the rotating blade 21 toward the axial direction together with the fluid passage 22. The elastic valve portion 31a of the seal member 3 is inserted into the vertical hole 22a. This is a configuration example in which the fluid passage 22 is covered in the vertical hole 22a. In this case, the base portion 31b of the elastic valve portion 31a is formed thick so as to be press-fitted into the vertical hole 22a, and the seal member 3 is engaged in a state where it is press-fitted in the upper portion of the fluid passage 22 as shown in FIG. Has been stopped.

FIGS. 7A and 7B show a fourth example of the seal member 3.
An example is shown. The fourth embodiment is an example in which the sliding contact piece 39 is formed integrally with the third embodiment. That is, the seal member 3 includes the sliding contact portion 33, the elastic valve portion 31a, and the rotary blade 2
1 and a sliding contact piece 39 arranged along one end face of the first side. A long groove 2 formed on one end face of the rotating blade 21
9 is a configuration in which a sliding contact piece 39 is arranged. In this case, the length of the long groove 29 is set slightly smaller than the length of the sliding contact piece 39. Therefore, the sliding contact piece 39 has the same function as the sliding contact portion 38 of the second embodiment, that is, the sliding contact piece 39 also elastically contacts the bottom surface of the cup shape, and in addition to the sealing property of the portion being reliably obtained, The seal member 3 is urged in a direction protruding from the tip end surface of the rotary wing 21. With this biasing force, the sealing property of the sliding contact portion 33 can be reliably obtained.

FIG. 8 is a transverse sectional view of a fluid pressure damper according to a fifth embodiment of the present invention, and FIG. 9 is a longitudinal sectional view of a main part. In addition,
The fifth embodiment is an example in which the fluid pressure damper is provided with a rotation stopping mechanism, and the same members or parts as those in the first embodiment are denoted by the same reference numerals, and only the main part will be described. Also, FIG. 1, FIG. 3,
FIG. 4 and its description are common to the fluid pressure damper of the fifth embodiment. The rotation stopping mechanism 7 is assembled around the shaft 2 in contact with the inner end surface of the closing lid 5. A spring member 71 mounted around the shaft 2, and a spring member 71 provided on a part of the spring member 71 and provided at a tip thereof A spring piece 73 for locking having a claw 72;
A locking groove 17 provided on the inner wall of the casing 1. The spring member 71 has a groove 74 provided on the inner diameter, and the groove 74 is engaged with the key portion 26 protruding from the outer peripheral portion of the shaft 2 near the large-diameter end surface to prevent rotation.

[0024]

The function of the fifth embodiment is such that when the shaft 2 rotates, the claw 72 of the spring piece 73 enters the locking groove 17 and engages removably. The spring force of the spring piece portion 73 and the engaging force between the claw portion 72 and the locking groove 17 act as a resistance to the rotational moment applied to the shaft 2, thereby preventing the shaft 2 from rotating. That is, the rotation stopping mechanism 7
The claw 72 of the spring member 71 that rotates integrally with the shaft 2 is engaged with the locking groove 17 on the casing 1 to prevent rotation, and the shaft 2 is rotated against the spring force and the engaging force to rotate the spring. Member 7
The rotation stop is released by releasing the lock between the first claw portion 72 and the locking groove 17. Such a rotation stopping mechanism 7 for the shaft 2
For example, this is used when a lid or the like connected to the shaft hole 24 via a shaft is in an open state, and it is desired to prevent the cover from inadvertently falling down from this open state and not closing.

In this configuration, a locking groove 17 is provided on the extension of the inner wall of the casing 1 near the closing lid 5, and a claw portion between the inner wall and the shaft 2 and engageable with the locking groove 17. Since the spring member 71 provided with the shaft 72 is fixed to the shaft 2 so as to rotate integrally therewith, a conventional rotation stopping mechanism in which a ball biased by a coil spring is engaged with a concave portion is provided. There is no need to form a hole or the like for accommodating a coil spring, and the claw portion 72 corresponding to a ball is formed integrally with the spring member 71, so that the number of parts can be reduced. Is excellent.

FIGS. 10 and 11 show a fluid pressure damper according to a sixth embodiment of the present invention. FIG. 10 is a cross-sectional view of a section including a section of a rotary wing 21, and FIG. FIG. The sixth embodiment is an example in which a braking force adjusting mechanism is added to the fluid pressure damper.
The same members or parts as in the embodiment are denoted by the same reference numerals, and only the main part will be described. Also, FIGS. 1, 3, 4, 9 and the description thereof are common to the fluid pressure damper of the sixth embodiment.
The braking force adjusting mechanism 8 includes a gap 27a between the shaft 2 and the bottom surface of the casing 1 for varying the braking force of the damper.
And the gap 27b of the shaft 2 with respect to the partition 11 can be adjusted.
And an elastic member 81 interposed therebetween. The elastic member 81 is made of synthetic rubber, has a disk shape having a predetermined thickness, and has a through hole corresponding to the inner flange of the closing lid 5 and a through hole corresponding to the bottle 62.

[0027]

In the braking force adjusting mechanism 8 described above, the elastic member 81 is interposed between the opening end face of the casing 1 and the closing lid 5 and the bolt 62 is tightened in the screw hole 15 of the casing 1. Thus, the shaft 2 is integrally pushed into the cylindrical chamber 14 by the pressing force of the closing lid 5. Then, the gaps 27a and 27b shown in FIGS. 10 and 11 are reduced, and the leakage or movement of the viscous fluid is reduced therefrom, and the damping force of the damper is increased. Conversely, when the bolts 62 are loosened, the closing lid 5 retreats in the axial direction due to the return force of the elastic member 81, and the gaps 27a and 27b are formed again in FIGS.
And the leakage or movement of the viscous fluid therefrom increases, and the damping force of the damper decreases. This gap 27
a and 27b are inversely proportional to the tightening force of the bolt 62, and even if the movement is slight, it is effective for adjusting the braking force.

In this configuration, the elastic member 81 interposed between the opening-side end face of the casing 1 and the closing lid 5 is
The size of the gaps 27 a and 27 b is changed according to the tightening force of the bolt 62. The width of the rotor 21 and the width of the partition 11 are matched, and the end face of the rotor 21 is pressed against the bottom end face of the casing 1 or the inner end face of the closing lid 5 so as to contact the end face of the cylindrical chamber 17. If the rotating blade 21 and the counterpart member are tightened with bolts, the fluid leaking from the clearances 27a and 27b when the rotating blade 21 rotates becomes small. Therefore, examples of such adjustment include a case where the sliding portion 33 of the seal member 3 that abuts against the inner wall of the casing 1 is worn, and a case where the damper action is reduced due to a decrease in fluid viscosity. In addition, the rotating blades 2 are intentionally or worn due to wear of the members.
When the gaps 27a and 27b between the first member and the mating member are large,
Fluid leakage from the gaps 27a and 27b increases.
Even in such a case, correction can be easily made.

[0029]

As described above, the fluid pressure damper according to the present invention has a simple structure with a one-way valve attached to the rotor, so that a damper with excellent performance can be provided at low cost. The one with the damper braking force adjustment function can compensate for changes in damper performance due to temperature changes and wear, so that it always has optimal damper performance and can have a longer life, which can be expected to expand applications. . In addition, since the shaft rotation stopping function minimizes the number of parts and can reduce the installation space, there is an effect that compactness and good assemblability are improved.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a hydraulic damper according to a first embodiment of the present invention together with its operation.

FIG. 2 is a cross-sectional view of the hydraulic damper.

FIG. 3 is a perspective view showing a rotating blade portion of the fluid pressure damper.

FIG. 4 is a sectional view showing a seal member of the fluid pressure damper and a modified example thereof.

FIG. 5 is a main part view showing a second embodiment in which the seal member has an additional function.

FIG. 6 is a main part view showing a third embodiment in which the seal member has an additional function.

FIG. 7 is a main part view showing a fourth embodiment in which the seal member has an additional function.

FIG. 8 is a sectional view showing a fifth embodiment in which a rotation stopping mechanism is added to the fluid pressure damper.

FIG. 9 is a sectional view showing a structure of the rotation stopping mechanism.

FIG. 10 is a sectional view showing a sixth embodiment in which a braking force adjusting mechanism is added to the fluid pressure damper.

FIG. 11 is a sectional view showing a structure of the braking force adjusting mechanism.

FIG. 12 is a sectional view of a main part showing two examples of a conventional fluid pressure damper.

[Explanation of symbols]

1 is a casing, 11 is a partition, 17 is a locking groove, 2 is a shaft, 21 is a rotor, 22 is a fluid passage, 22a is a vertical hole, 3 is a sealing member, 31 and 31a are elastic valve parts, and 33 and 38 are sliding contact parts. , 39 are sliding contact pieces 5 are closed lids 62 are bolts 7 are rotation preventing mechanisms, 71 is a spring member, 72 is a claw portion 8 is a braking force adjusting mechanism, and 81 is an elastic member.

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F16F 9/14 F16F 9/56 A47K 13/12 E05F 3/14

Claims (4)

(57) [Claims] 1. A fluid pressure damper in which a shaft provided with a rotating blade is rotatably combined with a cylindrical chamber of a casing having a partition wall protruding from an inner wall, and a viscous fluid is filled therein. providing one, the sliding contact portion in contact with the inner wall of the casing covers the front end face of the rotor blades, and one covering the side opening length schistose bullet <br/> of valve portion of the fluid passage, the other side of said fluid passage Short piece hooked on
A seal member having a substantially U- shaped cross-section integrally formed with a lock member having a shape like a cross section , wherein the seal member hooks the lock member on the other side of the rotor blade.
The elastic valve portion is attached to the rotor in this state and is rotatable integrally with the rotor, and receives the fluid pressure of the viscous fluid entering through the other port of the fluid passage only in one rotation of the shaft. A fluid pressure damper, which oscillates to open one side opening of a fluid passage. 2. A casing cylinder having a partition wall protruding from an inner wall.
When a shaft with rotating blades is rotatably combined with the chamber
Both the hydraulic damper viscous fluid-filled, with the flow fluid path to the rotor blade, while the Ru provided vertical holes leading to the fluid passage toward the distal end surface of the rotor blades in the axial direction, of the rotor blade A sealing member having a substantially T-shaped cross section, which integrally forms a sliding contact portion that covers the front end surface and contacts the inner wall of the casing and an elastic valve portion that is inserted into the vertical hole and covers the fluid passage in the vertical hole. has, in a state where the sealing member is inserted an elastic valve portion to the vertical hole
It is assembled with the rotor and can rotate integrally with the rotor.
And the elastic valve section is rotated only in one direction of the shaft.
Receives the fluid pressure of viscous fluid entering through the other port of the fluid passage.
To open one side of the fluid passage.
Features a hydraulic damper. 3. The seal member has a sliding contact piece disposed along one end face of the rotating blade, and is urged by the sliding contact piece in a direction protruding from a tip end surface of the rotating blade. The fluid pressure damper according to claim 2 . 4. The casing has a substantially cup shape,
With a closing lid bolted to the cup-shaped opening side, an elastic member is interposed between the cup-shaped opening end face and the end face of the closing lid, and according to the tightening force of the bolt,
The fluid pressure damper according to any one of claims 1 to 3 , further comprising a braking force adjusting mechanism capable of changing an axial position of the shaft and the rotor with respect to the cylindrical chamber of the casing.