JP2013050174A - Oil damper, and building structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To allow a piston to be moved through a cylinder slowly from a neutral position to a maximum amplitude position under a large damping force, and quickly from the maximum amplitude position to the neutral position without receiving the damping force.SOLUTION: There are included: a cylinder 2 with oil enclosed; a piston 5 that partitions the inside of the cylinder into a first oil chamber 3 and a second oil chamber 4; piston rods 6, 7 that protrude out of the piston 5; pressure-regulating valves 10, 11 placed in the piston 5 to make the first oil chamber 3 communicate with the second oil chamber 4, with the oil in the cylinder passing therethrough to apply the damping force to the piston as a result of displacement of the piston 5 from the neutral position; a notched oil flow path 17 formed in the inner wall of the cylinder that allows the oil to move between the first oil chamber 3 and the second oil chamber 4 while the piston 5 returns to the neutral position; an unaxial flow path 12; unidirectional flow paths 13, 14; and check valves 15, 16.

Description

  The present invention relates to an oil damper and a building structure, and more particularly, to an oil damper that damps vibrations using oil resistance generated by a piston that moves in a cylinder, and a building structure using the same.

As a device for buffering and attenuating vibrations in building structures and equipment, there has been proposed an oil damper that utilizes the resistance of oil passing through an orifice as the piston moves in the cylinder. In such an oil damper, various devices have been devised in order to make the damping characteristic appropriate in accordance with the speed and displacement of the piston in the cylinder.
In Patent Document 1, a predetermined damping force, a damper restoring force that gradually decreases with a predetermined damping force and a decreasing gradient as the deformation increases in a deformation region between the reduction start deformation point and the stroke end is configured. An oil damper is described (see paragraphs 0014 to 0016, FIGS. 4 and 5).
Further, in Patent Document 2, a cylinder filled with hydraulic oil is provided, and the cylinder is slid by the action of an external force, and the cylinder is defined as a first chamber and a second chamber. The piston, the first chamber and the second chamber communicate with each other, the hydraulic oil in the cylinder passes through the displacement of the piston, and generates a drag force. The piston is bypassed to the cylinder. The first chamber communicates with the second chamber when the displacement of the piston is not more than a predetermined length from the reference position, and the opening is blocked by the piston when the piston is displaced more than the predetermined length. And an oil damper comprising the communication passage (refer to the claims and FIGS. 2 to 4).

JP 2006-183250 A JP-A-1-320341

In a building, particularly a high-rise building, a vibration damping device including the above-described oil damper or the like is disposed in order to reduce shaking caused by seismic waves. Such a vibration damping device attenuates the vibration of the building due to the seismic wave and reduces the damage caused by the shaking of the building.
However, even in a high-rise building in which such a vibration control device is arranged, shaking with a large amplitude occurs on the high-rise floor. In high-rise buildings with seismic control devices, damage to buildings due to earthquakes is avoided, but swaying due to large amplitudes at low frequencies may cause discomfort and fear to residents.
That is, in such a building, when moving from the neutral position to the maximum amplitude, the vibration is controlled and shakes slowly, and when returning from the maximum amplitude to the neutral position, the vibration is also controlled and shaken slowly in the same manner as before. In such a case, the resident has no discomfort or fear of slow swinging in the past, but has discomfort or fear of slow swinging of the building when returning.
In order to reduce such discomfort and fear, it is necessary to make it possible to quickly perform the damping characteristics of the oil damper used in the vibration control device during the operation corresponding to the restoration of the building. However, the oil damper described in Patent Literature 1 and Patent Literature 2 cannot realize such a damping characteristic.
Therefore, according to the present invention, when the piston is forcibly reciprocated in the cylinder, the piston slowly moves with a large resistance from the neutral position to the maximum amplitude, and quickly moves without any resistance from the maximum amplitude to the neutral position. It is an object of the present invention to provide an oil damper that can be made, and a building structure using the oil damper.

In order to solve the above problems, an oil damper according to claim 1 is a hollow cylinder in which oil is enclosed, and is accommodated in the hollow part of the cylinder so as to be axially movable, and the first part is disposed in the hollow part. A piston partitioned into an oil chamber and a second oil chamber; a piston rod projecting from an axial end of the piston and slidably inserted into an insertion hole formed in an end of the cylinder; and the piston Damping that communicates between the first oil chamber and the second oil chamber, passes oil in the cylinder with displacement from the neutral position of the piston, and generates resistance when the piston moves A force generating means, disposed inside the piston, and when the piston returns from a state away from the neutral position to a neutral position, the oil bypasses the resistance force generating unit, and And communicating means for allowing the movement between the oil chamber and the second oil chamber, characterized in that it comprises a.
According to the oil damper of the present invention, when the piston moves from the neutral position to the maximum amplitude, the oil flows via the damping force generating means, so that the piston moves slowly. On the other hand, when the piston moves from the maximum amplitude to the neutral position, the oil passes through the communication means without receiving resistance, so that the piston quickly returns to the neutral position.

According to a second aspect of the present invention, in the oil damper according to the first aspect, the damping force generating means is a first unit that penetrates the piston in the axial direction and communicates the first and second oil chambers. Provided in the first axial passage and the second axial passage, and the oil flows from the first oil chamber into the second oil chamber. And a first pressure regulating valve that adjusts the flow rate of the oil when flowing into the first oil chamber from the second oil chamber, and the second axial passage, A second pressure regulating valve for preventing the second oil chamber from flowing into the first oil chamber and adjusting the flow rate of oil when flowing from the first oil chamber into the second oil chamber; The communication means has an outer end portion which is the pipe. A non-axial flow path that opens at the outer peripheral surface of the ton and whose inner end terminates inside the piston, and extends in one axial direction from the non-axial flow path and opens at one end face of the piston. A first one-way flow path communicating with the oil chamber, and a second one-way extending from the non-axial flow path to the other axial direction and opening at the other end face of the piston and communicating with the second oil chamber A flow path and an oil in the first oil chamber that is provided in the first one-way flow path and prevents the oil from flowing into the non-axial flow path via the first one-way flow path. A first check valve that allows inflow of oil from the non-axial flow path to the first oil chamber, and oil in the second oil chamber provided in the second one-way flow path Is prevented from flowing into the non-axial flow path via the second unidirectional flow path, and A second check valve that allows inflow of oil from the axial flow path to the second oil chamber; and a predetermined axial length on the inner wall of the cylinder, and regardless of the axial position of the piston. While it is always in communication with the outer diameter side opening of the non-axial flow path, when the piston is in the neutral position, it is in non-communication with any oil chamber, and the piston is in any shaft from the neutral position. And a notch oil passage that communicates with an oil chamber that is in a position opposite to the moving direction of the piston when displaced in the direction by a predetermined distance or more, and is located at a position outside the neutral position in the cylinder When moving in the cylinder to the neutral position side, the oil in the oil chamber on the moving direction side flows in the notch oil flow path, the non-axial flow path, and the unidirectional flow on the opposite side of the moving direction. It is configured to flow into the oil chamber on the side opposite to the moving direction via a path and a check valve disposed in the one-way flow path.
According to the oil damper of the present invention, when the piston moves from the neutral position to the maximum amplitude, the oil flows through the pressure regulating valve in the axial through flow path, so that the piston moves under a predetermined resistance. On the other hand, when the piston moves from the maximum amplitude to the neutral position, the oil passes through the notch oil passage formed in the cylinder, the non-axial passage, the one-way passage resistance, and the check valve without receiving resistance. Therefore, the piston returns to the neutral position without receiving resistance. Therefore, the piston can be moved slowly from the neutral position to the maximum amplitude, and can be moved quickly from the maximum amplitude to the neutral position.
Further, according to the oil damper according to the present invention, when the movement of the piston is within a predetermined distance from the neutral position, the oil does not flow through the notched oil flow path, so that the oil passes through the pressure regulating valve at the time of forward and return. . For this reason, a predetermined resistance is given to the reciprocating motion of the piston.

  According to a third aspect of the present invention, in the oil damper according to the first aspect, the damping force generating means is a first unit that penetrates the piston in the axial direction and communicates the first and second oil chambers. Provided in the first axial passage and the second axial passage, and the oil flows from the first oil chamber into the second oil chamber. And a first pressure regulating valve that adjusts the flow rate of the oil when flowing into the first oil chamber from the second oil chamber, and the second axial passage, A second pressure regulating valve for preventing the second oil chamber from flowing into the first oil chamber and adjusting the flow rate of oil when flowing from the first oil chamber into the second oil chamber; The communication means includes the first shaft. A through-sliding hole penetrating between both axial end surfaces of the piston avoiding the through-through channel and the second axial through-channel, and fixed in the cylinder so as to be slidable into the through-sliding hole A columnar member to be arranged, a non-axial flow path having an outer end opened at the outer peripheral surface of the columnar member, and an inner end terminated inside the piston, and extends from the non-axial flow path to one axial direction. A first one-way flow path that opens at one end face of the piston and communicates with the first oil chamber, and extends from the non-axial flow path to the other axial direction and opens at the other end face of the piston. A second one-way flow path communicating with the second oil chamber; and the oil in the first oil chamber provided in the first one-way flow path via the first one-way flow path. The first oil is prevented from flowing into the non-axial flow path and from the non-axial flow path. A first check valve that allows the oil to flow into the second one-way flow path, and the oil in the second oil chamber passes through the second one-way flow path. A second check valve that prevents the oil from flowing into the non-axial flow path and allows oil to flow from the non-axial flow path into the second oil chamber; and a predetermined outer periphery of the columnar member. Any oil chamber is formed when the piston is in a neutral position while being always in communication with the outer diameter side opening of the non-axial flow path regardless of the axial position of the piston. A notch oil flow path that communicates with an oil chamber in a position opposite to the moving direction of the piston when the piston is displaced by a predetermined distance or more in any axial direction from the neutral position. Configured with the cylinder -When the piston in the position deviated from the neutral position in the cylinder moves to the neutral position side in the cylinder, the oil in the oil chamber on the moving direction side moves in the notched oil flow path, the non-axial flow path, It is configured to flow into the oil chamber on the opposite side to the moving direction via a one-way flow path opposite to the direction and a check valve arranged in the one-way flow path.

According to the oil damper of the present invention, when the piston moves from the neutral position to the maximum amplitude, the oil flows through the pressure regulating valve in the axial through flow path, so that the piston moves under a predetermined resistance. On the other hand, when the piston moves from the maximum amplitude to the neutral position, the oil passes through the notched oil passage, the non-axial passage, the one-way passage resistance, and the check valve of the columnar member without receiving resistance. The piston returns to the neutral position without receiving resistance. Therefore, the piston can be moved slowly from the neutral position to the maximum amplitude, and can be moved quickly from the maximum amplitude to the neutral position.
Further, according to the oil damper according to the present invention, when the movement of the piston is within a predetermined distance from the neutral position, the oil does not flow through the notch oil passage. pass. For this reason, a predetermined resistance is given to the reciprocating motion of the piston. Further, according to the oil damper according to the present invention, it is only necessary to replace the columnar member formed with the notched oil flow path having a different shape in order to change the characteristics of the oil damper. A damper can be manufactured.

According to a fourth aspect of the present invention, in the oil damper according to any one of the first to third aspects, a connecting member that connects the oil damper to an external member is disposed on the cylinder and the piston rod. It is characterized by.
According to the oil damper concerning the present invention, an oil damper can be easily arranged in a building etc. by attaching a connecting member to a structural member of a building.

According to a fifth aspect of the present invention, the oil damper according to any one of the first to fourth aspects is disposed between structural members of a building, and when the building vibrates, from the amplitude end of the building to the neutral position. This time is shorter than the time from the neutral position to the amplitude end.
According to the building structure according to the present invention, it is possible to shorten the time until it returns from the amplitude end to the neutral position at the time of vibration of the building, compared to the time from the neutral position to the amplitude end, thereby reducing discomfort and fear of the resident. be able to.

As described above, according to the oil damper of the present invention, when the piston moves in the cylinder, the piston slowly moves with a large damping force from the neutral position to the maximum amplitude, and a small damping force from the maximum amplitude to the neutral position. To move quickly.
Further, according to the building structure according to the present invention, when the building vibrates such as an earthquake, the building can be moved slowly from the neutral position to the maximum amplitude, and can be quickly returned from the maximum amplitude to the neutral position. , Resident discomfort and fear can be reduced.

It is sectional drawing which shows the oil damper which concerns on 1st Embodiment. The state of operation | movement of the oil damper is shown, (a)-(e) is sectional drawing which shows operation | movement of an oil damper with time. It is a graph which shows the operating characteristic of the oil damper. It is sectional drawing which shows the modification of the oil damper which concerns on 2nd Embodiment. It is sectional drawing of the oil damper which concerns on 3rd Embodiment. The state of operation | movement of the oil damper is shown, (a)-(e) is sectional drawing which shows operation | movement of an oil damper with time. It is a graph which shows the operating characteristic of the oil damper. It is a schematic diagram which shows the building structure which concerns on embodiment. It is a schematic diagram which shows the building structure which concerns on embodiment. It is a schematic diagram which shows the building structure which concerns on embodiment. It is a schematic diagram which shows the building structure which concerns on embodiment. It is a schematic diagram which shows the building structure which concerns on embodiment.

Hereinafter, an oil damper and a building structure according to the present invention will be described based on the embodiments shown in the drawings.
<Oil damper according to the first embodiment>
Hereinafter, the oil damper according to the first embodiment will be described. FIG. 1 is a cross-sectional view showing an oil damper according to the first embodiment. The oil damper 1 according to the first embodiment includes a hollow cylinder 2 in which oil is sealed, and a piston 5 accommodated in the hollow portion of the cylinder 2 so as to be movable in the sliding axis O direction. The piston 5 partitions the inside of the hollow part into a first oil chamber 3 and a second oil chamber 4.
Insertion holes 2a and 2b are formed at both ends of the cylinder 2, and piston rods 6 are inserted from both axial ends of the piston 5 into the insertion holes 2a and 2b so as to be slidable and oil-tight. , 7 are projected.

Further, the piston 5 has a first axial through passage 8 and a second shaft that pass through the piston in the direction of the sliding axis O to communicate the first oil chamber 3 and the second oil chamber 4. A directional through channel 9 is formed.
The first axial through passage 8 prevents oil from flowing from the first oil chamber 3 into the second oil chamber 4, and the oil from the second oil chamber 4 to the first oil chamber 4. A first pressure regulating valve 10 that adjusts the flow rate of oil when flowing into the cylinder 3 is disposed.
The second axial passage 9 prevents oil from flowing from the second oil chamber 4 into the first oil chamber 3, and the oil flows from the first oil chamber 3 to the second oil passage 3. A second pressure regulating valve 11 that adjusts the flow rate of the oil when flowing into the oil chamber 4 is disposed.

The first axial through flow path 8, the second axial through flow path 9, the first pressure regulating valve 10, and the non-axial flow path 12 constitute a resistance applying unit.
The first pressure regulating valve 10 and the second pressure regulating valve 11 include valve bodies 10a and 11a and springs 10b and 11b, respectively. For example, the resistance due to oil is adjusted to be proportional to the moving speed of the piston 5. In addition, the 1st pressure regulation valve 10 and the 2nd pressure regulation valve 11 can change the number of formation, the shape of a valve body, and the strength of a spring according to the damping characteristic calculated | required.
Further, a non-axial flow path 12 is opened in the piston 5. The non-axial flow path 12 is formed such that the outer diameter side opening 12 a opens at the outer peripheral surface 5 a of the piston 5 and the inner end 12 b terminates inside the piston 5. Further, the piston 5 has a first one-way channel 13 that extends from the non-axial channel 12 toward the first oil chamber 3, opens at the end surface of the piston 5, and communicates with the first oil chamber 3. Then, a second one-way channel 14 extending from the non-axial channel 12 toward the second oil chamber 4 and opening at the end face of the piston and communicating with the second oil chamber 4 is formed. A plurality of first unidirectional flow paths 13 and second unidirectional flow paths 14 are formed in the piston 5 as necessary.

The first unidirectional flow path 13 prevents oil in the first oil chamber 3 from flowing into the non-axial flow path 12 via the first unidirectional flow path 13 and is non-axial. A first check valve 15 that allows inflow of oil from the directional flow path 12 to the first oil chamber 3 is disposed.
Further, the second one-way flow path 14 prevents oil in the second oil chamber 4 from flowing into the non-axial flow path 12 via the second one-way flow path 14, and A second check valve 16 that allows inflow of oil from the non-axial flow path 12 to the second oil chamber 4 is disposed. The check valves 15 and 16 are configured such that, for example, the valve bodies 15a and 16a are urged in a closing direction by a spring (not shown).
For convenience of illustration and explanation, the first and second unidirectional flow paths 13 and 14 are omitted as lines, but in practice, the first and second axial through flow paths 8, 9 is a flow path having a predetermined diameter as in FIG. Further, the first and second check valves 15 and 16 are arranged at, for example, an intermediate position between the first and second one-way flow paths 13 and 14 to advance and retreat in the axial direction, thereby causing each one-way flow. It is configured to open and close.

The pressure required for the first check valve 15 and the second check valve 16 to pass the oil is the pressure required for the first pressure control valve 10 and the second pressure control valve 11 to pass the oil. Is set smaller than. Further, the oil hardly receives resistance when passing through the first check valve 15 and the second check valve 16.
Further, the cylinder 2 has a notch oil which is formed on the inner wall 2c over a predetermined axial length and is always in communication with the outer diameter side opening 12a of the non-axial flow path 12 regardless of the axial position of the piston 5. A flow path 17 is formed. When the piston 5 is in the neutral position, the recessed cutout oil flow path 17 is not in communication with the first oil chamber 3 and the second oil chamber 4, and the piston 5 is in any axial direction from the neutral position. When moving by the displacement amount S, the oil chamber communicates with the piston 5 in the opposite direction to the moving direction.
In the oil damper 1 according to the first embodiment, the displacement amount S is set to “0”. For this reason, when the piston 5 is in the neutral position, the notch oil flow path 17 is blocked, but when the piston 5 moves in the axial direction even slightly from the neutral position, the notch oil flow path 17 It will communicate with the oil chamber on the opposite side to the moved side. Note that the displacement amount S can be set according to the required attenuation characteristic.

In the oil damper 1 according to the first embodiment, the non-axial flow path 12, the first unidirectional flow path 13, the second unidirectional flow path 14, the first check valve 15, and the second check valve. The valve 16 and the notch oil flow path 17 constitute a communication means.
With such a configuration, the oil damper 1 according to the first embodiment is configured such that when the piston 5 at a position deviated from the neutral position in the cylinder 2 moves in the cylinder 2 toward the neutral position, the moving direction leading side The oil in the oil chamber passes through the notch oil passage 17, the non-axial passage 12, the one-way passage opposite to the cylinder moving direction, and the check valve disposed in the one-way passage. It is configured to flow into the oil chamber opposite to the moving direction.

Next, the operation of the oil damper 1 according to the first embodiment will be described. FIG. 2 shows the state of operation of the oil damper according to the first embodiment, (a) to (e) are cross-sectional views showing the operation of the oil damper over time, and FIG. 3 is also the operation of the oil damper. It is a graph which shows a characteristic.
In this example, a state in which the piston rod 7 moves to the left and right along the sliding axis O from the state in which the piston 5 is in the neutral position (FIG. 2A) is subjected to an externally vibrating force. . The cylinder 2 is assumed to be fixed.
First, when the piston 5 receives a force (right (b) arrow A) in the right direction in the drawing and moves in the right direction, the oil in the second oil chamber 4 flows through the first axial through flow path 8, the first 1 passes through the pressure regulating valve 10 and moves to the first oil chamber 3. At this time, a predetermined damping force is generated when the oil passes through the first pressure regulating valve 10. For this reason, the piston 5 moves in the cylinder 2 while receiving a large damping force. At this time, the notch oil passage 17 is closed by the piston 5.
When the piston 5 receives a leftward force (arrow (c) arrow B) from the maximum amplitude position on the right side and moves leftward, the oil in the first oil chamber 3 flows into the notch oil passage 17, the non-axial shaft. It moves to the second oil chamber 4 via the directional flow path 12, the second unidirectional flow path 14, and the second check valve 16. At this time, the oil moves without receiving a great resistance. For this reason, the piston 5 moves in the cylinder 2 without receiving a damping force.

Next, when the piston 5 located at the neutral position moves to the left in response to the leftward force (arrow (d) arrow C), the oil in the first oil chamber 3 flows through the second axial through flow. It passes through the passage 9 and the second pressure regulating valve 11 and moves to the second oil chamber 4. A predetermined resistance force is generated when the oil passes through the second pressure regulating valve 11. For this reason, the piston 5 moves in the cylinder 2 while receiving a large damping force. At this time, the notch oil passage 17 is closed by the piston 5.
Further, when the piston 5 located at the left maximum amplitude position receives a force in the right direction (same (e) arrow D) and moves in the right direction, the oil in the second oil chamber 4 flows into the notch oil passage. 17, moves to the first oil chamber 3 via the non-axial flow path 12, the first one-way flow path 13, and the first check valve 15. At this time, the oil moves without receiving a great resistance. For this reason, the piston 5 moves in the cylinder 2 without receiving a damping force.
As described above, in the oil damper 1, when the piston 5 moves in the cylinder 2, the piston 5 moves slowly while receiving a large damping force from the neutral position to the maximum amplitude, and a small damping force is applied from the maximum amplitude to the neutral position. Receive and move quickly.

Next, the relationship between the displacement amount δ (mm) of the piston 5 of the oil damper 1 according to the first embodiment and the damping force Q (kN) will be described. FIG. 3 is a graph showing operating characteristics of the oil damper according to the first embodiment.
In the graph shown in FIG. 3, the maximum amplitude of the piston 5 is 20 mm (broken line), 10 mm (one-dot chain line), and 2 mm (solid line). In the oil damper 1 according to the first embodiment, when the piston 5 is displaced from the neutral position (displacement amount 0) in the right direction (the positive direction of δ) or the left direction (the negative direction of δ), a predetermined damping force is generated. On the other hand, when the piston 5 is moved from the maximum amplitude to the neutral position side, it can be seen that almost no damping force is generated.

<Oil damper according to the second embodiment>
Next, an oil damper according to a second embodiment will be described. FIG. 4 is a cross-sectional view showing an oil damper according to the second embodiment. In the oil damper 20, an eye nut (connection member) 21 is attached to the piston rod 7 as an attachment member to an external member, and an eye bolt (connection member) 24 is attached to the cylinder 2 via an attachment fitting 23. In the oil damper 1 according to this embodiment, the eye nut 21 is attached to the piston rod 7 with the screw portion 22.
According to the oil damper 20 according to the second embodiment, when the oil damper 20 is disposed on a structural member such as a building as a vibration damping member, the oil damper 20 can be easily joined with the eye nut 21 and the eye bolt 24. In addition, when attaching this oil damper 20 to a building, it is necessary to attach the oil damper 20 to a building in a neutral state. For this reason, it is desirable to form an elongate fixing hole in the mounting bracket for the oil damper 20 arranged in the building so that the mounting position of the oil damper 20 can be adjusted.

<Oil damper according to the third embodiment>
Next, an oil damper according to a third embodiment will be described. FIG. 5 is a cross-sectional view of an oil damper according to the second embodiment. The oil damper 30 according to the second embodiment is different from the oil damper 1 according to the first embodiment in the configuration of the communication means. The configuration of the damping force applying means is the same as that of the oil damper 1 according to the first embodiment. In addition, the same code | symbol is attached | subjected to the same structural member as the oil damper 1 which concerns on 1st Embodiment, and the description is abbreviate | omitted.
The communication means constituting the oil damper 30 has the following configuration. The piston 5 is provided with a through sliding hole 31 penetrating between both end surfaces in the sliding axis O direction at a location avoiding the first axial through flow path 8 and the second axial through flow path 9. ing. Further, the cylinder 2 is provided with a columnar member 32 that is fixed inside the cylinder 2 and is slidable through the through-sliding hole 31 of the piston 5 and is penetrated while maintaining an oil-tight state. The through sliding hole 31 is arranged along an axis O1 parallel to the sliding axis O.
That is, the columnar member 32 penetrates through the through sliding hole 31 in a slidable and oiltight manner, and is fixed to the inner wall of the cylinder.
Furthermore, a non-axial flow path 33 is formed in the piston 5. The non-axial flow path 33 has an outer end that opens at the outer peripheral surface 32 a of the columnar member 32, and an inner end that terminates inside the piston 5. Further, the piston 5 extends in one axial direction from the non-axial flow path, opens at one end surface of the piston 5, and communicates with the first oil chamber 3. A second one-way flow path 14 that extends from the axial flow path 33 in the other axial direction and opens at the other end face of the piston 5 and communicates with the second oil chamber 4 is formed.

The first unidirectional flow path 13 prevents oil in the first oil chamber 3 from flowing into the non-axial flow path 33 via the first unidirectional flow path 13 and A first check valve 15 that allows oil to flow from the directional flow path 33 into the first oil chamber 3 is provided. Further, the second one-way flow path 14 prevents oil in the second oil chamber 4 from flowing into the non-axial flow path 33 via the second one-way flow path 14, and A second check valve 16 that allows inflow of oil from the non-axial flow path 33 to the second oil chamber 4 is disposed.
Each check valve 15, 16 is elastically biased in a direction to close each non-axial flow path by a spring (not shown) as necessary.
A notch oil passage 34 formed of a recess having a predetermined depth is formed on the outer peripheral surface of the columnar member 32. The notch oil passage 34 is formed over a predetermined axial length, and is always in communication with the outer diameter side opening 33a of the non-axial passage 33 regardless of the axial position of the piston 5, while the piston 5 When in the neutral position, none of the oil chambers 3 and 4 is in communication, and when the piston 5 is displaced from the neutral position in any axial direction by a predetermined distance (S: 5 mm in this example) or more, the moving direction of the piston It communicates with the oil chamber in the opposite direction.

That is, the non-axial direction flow path 33 is formed along the outer peripheral surface of the columnar member 32, and finally communicates with the notch oil flow path 34. The outermost end opening of the non-axial flow path 33 is closed by the outer peripheral surface of the cylinder.
With such a configuration, even when the piston 5 moves in any direction, when the piston 5 reciprocates within a predetermined distance S from the neutral position in the cylinder 2, the oil is supplied to the first pressure regulating valve 10 or the second pressure regulating valve 10. It passes through the pressure regulating valve 11.
On the other hand, when the piston 5 reciprocates beyond the predetermined distance S, when the piston 5 at a position deviated from the neutral position moves in the cylinder 2 to the neutral position side, the oil in the oil chamber on the moving direction side becomes the columnar member. 32 through the notch oil passage 34, the one-way passage opposite to the moving direction, and the check valve disposed in the one-way passage so as to flow into the oil chamber opposite to the moving direction. Composed.

Next, the operation of the oil damper 30 according to the third embodiment will be described. FIG. 6 shows the state of operation of the oil damper according to the third embodiment, and (a) to (e) are cross-sectional views showing the operation of the oil damper over time.
In this example, the piston 5 moves from the state where the piston 5 is in the neutral position (FIG. 6A), receiving a force oscillating left and right along the sliding axis O from the piston rod 7. The cylinder 2 is assumed to be fixed. The piston 5 moves with an amplitude of a predetermined distance (S: 5 mm) or more. When the piston 5 does not exceed the displacement amount S, the oil passes through the first pressure regulating valve 10 and the second pressure regulating valve 11 as the piston 5 moves in the left-right direction, and a predetermined resistance is applied to the piston 5. . The value of S is an appropriate value based on the maximum amplitude of vibration that gives damping.

First, when the piston 5 in the neutral position receives a force in the right direction in the figure (arrow (A) in FIG. 2B) and moves in the right direction, the oil in the second oil chamber 4 penetrates the first axial direction. The fluid passes through the flow path 8 and the first pressure regulating valve 10 and moves to the first oil chamber 3. When the oil passes through the first pressure regulating valve 10, a predetermined resistance force is generated. For this reason, the piston 5 moves in the cylinder 2 while receiving a large damping force. At this time, the notch oil passage 17 is closed by the piston 5.
When the piston 5 at the maximum amplitude position on the right side receives a leftward force (arrow (c), arrow B) and moves leftward, the oil in the first oil chamber 3 flows into the notch oil flow path 34, the non-axis. It moves to the second oil chamber 4 via the directional flow path 33, the second unidirectional flow path 14, and the second check valve 16. At this time, the oil moves without receiving a great resistance. For this reason, the piston 5 moves in the cylinder 2 without receiving a damping force.

Next, when the piston 5 in the neutral position receives a leftward force (arrow (d), arrow C) and moves to the left, the oil in the first oil chamber 3 flows through the second axial passage. 9. Passes through the second pressure regulating valve 11 and moves to the second oil chamber 4. When the oil passes through the second pressure regulating valve 11, a predetermined resistance force is generated. For this reason, the piston 5 moves in the cylinder 2 while receiving a large damping force. At this time, the notch oil passage 34 is closed by the piston 5.
Further, when the piston 5 located at the maximum amplitude position on the left side receives a force in the right direction (same (e) arrow D) and moves in the right direction, the oil in the second oil chamber 4 flows into the notch oil passage 34. The first oil chamber 3 is moved through the non-axial flow path 33, the first one-way flow path 13, and the first check valve 15. At this time, the oil moves without receiving a great resistance. For this reason, the piston 5 moves in the cylinder 2 without receiving a damping force.

Next, the relationship between the displacement amount δ (mm) of the piston 5 of the oil damper 30 and the damping force Q (kN) during the operation of the oil damper 30 according to the third embodiment will be described. FIG. 7 is a graph showing the operating characteristics of the oil damper 30 according to the second embodiment.
In the graph shown in FIG. 3, the maximum amplitude of the piston 5 is 20 mm (broken line), 10 mm (one-dot chain line), and 2 mm (solid line). In the oil damper 30, the displacement amount S is set to 5 mm, for example. In the oil damper 30 according to the second embodiment, when the piston 5 is displaced 10 mm or 20 mm in the right direction (positive direction of δ) or the left direction (negative direction of δ), a damping force Q is generated, and the piston 5 It can be seen that almost no damping force Q is generated when moving from the maximum amplitude to the opposite side.
Further, it can be seen that when the piston 5 is moved left and right by 2 mm which is 5 mm or less, the damping force Q is generated in any direction.

As described above, according to the oil damper 30 according to the third embodiment, a resistance force acts on the movement of the piston 5 in either direction of the reciprocating motion with respect to a small amplitude. For this reason, when the oil damper 30 is used for vibration control of a building structure, it is possible to effectively attenuate vibrations with minute amplitudes caused by traveling of the vehicle or the like. And with respect to vibration with a large amplitude, the return speed to the neutral position can be made quick to reduce the resident's discomfort and anxiety.
In the oil damper 30 according to the third embodiment, the shape and capacity of the notched oil flow path 34 may be changed in order to change the damping characteristic. In this case, it is only necessary to replace the columnar member 32 in which the notched oil passage 34 is formed, and the damping characteristic of the oil damper 30 can be easily changed.

<Embodiment of building structure>
Next, a building structure using the above-described oil damper will be described. The oil damper mentioned above can be arrange | positioned between the structures of a building, and the building structure provided with the vibration suppression function is realizable. 8 to 12 are schematic views showing the building structure according to the embodiment.
The building structure 40 shown in FIG. 8 uses the oil damper 1 as a bracing member 45 that connects between the ground 41 and the structural member 42 and between the structural members 42, 43, and 44 constituting each floor. .
Moreover, the building structure 50 shown in FIG. 9 arrange | positions the oil damper 1 via the two diagonal members 55 and 56 and the attachment member 57 between the ground 51 and the structural member 52, and two or more floors of each floor are also provided. The oil damper 1 is disposed between the structural members 52, 53, and 54 via the diagonal members 55 and 56.
In the building structure 60 shown in FIG. 10, the oil damper 1 is disposed between the ground 61 and the structural member 62 via the mounting members 55 and 56, and the structural members 62, 63, and 64 of each floor are arranged at least two floors. The oil damper 1 is disposed via attachment members 65 and 66.
In an example of a building structure 70 shown in FIG. The oil damper 1 is disposed via toggle members 75 and 76 between them.
The building structure 80 shown in FIG. 12 has a seismic isolation structure. In this building structure 80, a laminated rubber isolator 83 and an oil damper 1 are arranged between a ground 81 and a foundation member 82.

In each of the above examples, the oil damper according to the first embodiment is used. However, oil dampers according to the second and third embodiments and other modifications can be used.
As described above, the oil damper can be arranged in the building structure in various modes. Moreover, the arrangement | positioning aspect of an oil damper is not restricted to said each example, It can use for a building structure with various forms as needed. In such a building structure, when the building vibrates such as an earthquake, the building can be moved slowly from the neutral position to the maximum amplitude, and can be quickly returned from the maximum amplitude to the neutral position. Discomfort and fear can be reduced.

DESCRIPTION OF SYMBOLS 1 Oil damper, 2 Cylinder, 2a, 2b Insertion hole, 2c Inner wall, 3rd 1st oil chamber, 4th 2nd oil chamber, 5 Piston, 5a outer peripheral surface, 6, 7 Piston rod 8 1st axial direction through flow Path, 9 second axial passage, 10 first pressure regulating valve, 11 second pressure regulating valve, 12 non-axial flow path, 12a outer end, 12b inner end, 13 first one-way flow Path, 14 second one-way flow path, 15 first check valve, 16 second check valve, 17 notch oil flow path

Claims (5)

A hollow cylinder with oil inside,
A piston which is accommodated in the hollow portion of the cylinder so as to be axially movable and partitions the hollow portion into a first oil chamber and a second oil chamber;
A piston rod projecting from the axial end of the piston and slidably inserted into an insertion hole formed in the end of the cylinder;
Located in the piston, communicates the first oil chamber and the second oil chamber, and the oil in the cylinder passes along with the displacement from the neutral position of the piston, generating a resistance force when the piston moves A damping force generating means,
The oil is disposed inside the piston, and when the piston returns from the state away from the neutral position to the neutral position, the oil bypasses the resistance generating portion, and the first oil chamber and the second oil chamber Communication means allowing movement between
Oil damper characterized by comprising The damping force generating means is
A first axial through passage and a second axial through passage that pass through the piston in the axial direction to communicate the first and second oil chambers;
The oil is provided in the first axial passage, and prevents the oil from flowing into the second oil chamber from the first oil chamber, and from the second oil chamber to the first oil chamber. A first pressure regulating valve for adjusting the flow rate of oil when flowing into
Provided in the second axial passage, and prevents the oil from flowing into the first oil chamber from the second oil chamber, and from the first oil chamber to the second oil chamber. A second pressure regulating valve that adjusts the flow rate of oil when flowing into
The communication means is
A non-axial flow path having an outer end opened at the outer peripheral surface of the piston and an inner end terminated inside the piston;
A first one-way channel extending in one axial direction from the non-axial channel and opening at one end face of the piston and communicating with the first oil chamber;
A second one-way flow path extending from the non-axial flow path to the other axial direction and opening at the other end face of the piston and communicating with the second oil chamber;
The oil provided in the first one-way flow path prevents oil in the first oil chamber from flowing into the non-axial flow path via the first one-way flow path, and A first check valve that allows inflow of oil from an axial flow path into the first oil chamber;
The oil provided in the second one-way flow path prevents oil in the second oil chamber from flowing into the non-axial flow path via the second one-way flow path, and A second check valve that allows inflow of oil from the axial flow path into the second oil chamber;
The cylinder inner wall is formed over a predetermined axial length and is always in communication with the outer diameter side opening of the non-axial flow path regardless of the axial position of the piston, while the piston is in a neutral position Sometimes the oil chamber is not in communication with any oil chamber, and when the piston is displaced from the neutral position in any axial direction by a predetermined distance or more, the notched oil communicates with the oil chamber in the position opposite to the moving direction of the piston. And a flow path,
When a piston in a position deviating from the neutral position in the cylinder moves to the neutral position side in the cylinder, the oil in the oil chamber on the moving direction side is the notched oil flow path, the non-axial flow path, The unidirectional flow path opposite to the moving direction and a check valve arranged in the unidirectional flow path are configured to flow into the oil chamber opposite to the moving direction. The oil damper according to 1. The damping force generating means is
A first axial through passage and a second axial through passage that pass through the piston in the axial direction to communicate the first and second oil chambers;
The oil is provided in the first axial passage, and prevents the oil from flowing into the second oil chamber from the first oil chamber, and from the second oil chamber to the first oil chamber. A first pressure regulating valve that adjusts the flow rate of oil when it flows into
Provided in the second axial passage, and prevents the oil from flowing into the first oil chamber from the second oil chamber, and from the first oil chamber to the second oil chamber. And a second pressure regulating valve that adjusts the flow rate of oil when flowing into
The communication means is
A through-sliding hole penetrating between both axial end surfaces of the piston avoiding the first axial through-flow path and the second axial through-flow path;
A columnar member fixed in the cylinder and slidably disposed in the through sliding hole;
A non-axial flow path having an outer end opened at the outer peripheral surface of the columnar member, and an inner end terminated inside the piston;
A first one-way channel extending in one axial direction from the non-axial channel and opening at one end face of the piston and communicating with the first oil chamber;
A second one-way flow path extending from the non-axial flow path to the other axial direction and opening at the other end face of the piston and communicating with the second oil chamber;
The oil provided in the first one-way flow path prevents oil in the first oil chamber from flowing into the non-axial flow path via the first one-way flow path, and A first check valve that allows inflow of oil from an axial flow path into the first oil chamber;
The oil provided in the second one-way flow path prevents oil in the second oil chamber from flowing into the non-axial flow path via the second one-way flow path, and A second check valve that allows inflow of oil from the axial flow path into the second oil chamber;
Any oil is formed on the outer periphery of the columnar member over a predetermined axial length, and is always in communication with the non-axial flow path regardless of the axial position of the piston, while the piston is in a neutral position. A notch oil flow path that communicates with an oil chamber in a position opposite to the moving direction of the piston when the piston is displaced by a predetermined distance or more in any axial direction from the neutral position. Configured with
When a piston in a position deviating from the neutral position in the cylinder moves to the neutral position side in the cylinder, the oil in the oil chamber on the moving direction side is the notched oil flow path, the non-axial flow path, The unidirectional flow path opposite to the moving direction and a check valve arranged in the unidirectional flow path are configured to flow into the oil chamber opposite to the moving direction. The oil damper according to 1.   The oil damper according to any one of claims 1 to 3, wherein a connecting member for connecting the oil damper to an external member is disposed on the cylinder and the piston rod.   The oil damper according to any one of claims 1 to 4 is arranged between structural members of a building, and when the building vibrates, the time from the amplitude end of the building to the neutral position is returned to the amplitude from the neutral position. An architectural structure characterized by a shorter time to reach the edge.

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