JP2017129201A - Fluid damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fluid damper capable of easily implementing assembly work and obtaining a relatively great damping force by reducing conventional partition walls for dividing a fluid chamber filled with a working fluid.SOLUTION: First and second pistons that are linked with each other while interposing an interval in an axial direction therebetween are freely movable in the axial direction inside of a cylinder. Inside of the cylinder, at least a first fluid chamber that is separated by the first piston, a second fluid chamber that is separated by the first and second pistons and a third fluid chamber that is separated by the second piston are provided and the first to third fluid chambers are filled with working fluids. A first communication path for causing the working fluid to flow between the first fluid chamber and the second fluid chamber is communicated to the first and second fluid chambers, and a second communication path for causing the working fluid to flow between the second fluid chamber and the third fluid chamber is communicated to the second and third fluid chambers.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a fluid damper for suppressing vibration of a structure.

  Conventionally, what was disclosed by patent document 1, for example as this kind of fluid damper is known. The fluid damper includes a cylinder filled with a working fluid, a first piston and a second piston provided in the cylinder so as to be slidable in the axial direction, and extends in the axial direction and is attached to the first and second pistons. In addition, a piston rod that is movable in the axial direction with respect to the cylinder is provided. The cylinder includes a peripheral wall extending in the axial direction, a first side wall and a second side wall integrally provided at one end and the other end in the axial direction of the peripheral wall, and a center between the first side wall and the second side wall in the peripheral wall. It is comprised by the partition wall etc. which were integrally provided in. In the cylinder, a first chamber defined by the peripheral wall, the first side wall and the partition wall and a second chamber defined by the peripheral wall, the partition wall and the second side wall are provided.

  The working fluid is filled in the first and second chambers, and the first and second pistons are slidably provided in the first and second chambers, respectively. The first chamber is partitioned into a first fluid chamber and a second fluid chamber by a first piston, and the second chamber is partitioned into a third fluid chamber and a fourth fluid chamber by a second piston. The first piston is provided with a first orifice that communicates the first and second fluid chambers with each other, and the second piston is provided with a second orifice that communicates the third and fourth fluid chambers with each other.

  In the conventional fluid damper having the above-described configuration, when the piston rod moves in the axial direction with respect to the cylinder due to the external force, the first and second pistons slide along the first and second chambers accordingly. As the fluid passes through the first and second orifices while being pressed by the first and second pistons, a damping force is generated. In the conventional fluid damper, it is noted that the damping force of this type of fluid damper increases as the pressure receiving area of the working fluid in the piston increases, and the first and first pistons are reduced in size while reducing the piston in the radial direction. A larger damping force is obtained according to the pressure receiving area of two pistons composed of two pistons.

  Moreover, the conventional fluid damper is assembled as follows, for example. That is, as a cylinder, a pair of split cylinders that can be joined to each other in the radial direction is prepared, and the first and second pistons are accommodated in the first and second chambers, respectively, and the piston rod From both sides in the radial direction. Next, a pair of split cylinders are joined to each other via a seal to form a cylinder. Next, after the working fluid is filled into the first and second chambers via the filling holes formed in the divided cylinders, the filling holes are closed. Next, the pair of divided cylinders joined to each other is accommodated inside the cylindrical cover.

JP 2014-163696 A

  However, in the conventional fluid damper, as described above, in order to provide the first and second pistons in the first and second chambers of the cylinder, a partition wall integral with the cylinder is provided. For this reason, when assembling the fluid damper, a pair of divided cylinders having a complicated shape in which the cylinder is divided in the radial direction must be prepared. In addition, a specially shaped seal that matches the joint surface must be provided on the entire joint surface of the pair of split cylinders. From the above, in the conventional fluid damper, the assembling work becomes very complicated.

  The present invention has been made to solve the above-described problems, and can reduce the number of conventional partition walls for partitioning a fluid chamber filled with a working fluid, thereby facilitating assembly work. An object of the present invention is to provide a fluid damper capable of obtaining a relatively large damping force.

  In order to achieve the above object, a fluid damper according to a first aspect of the present invention includes a cylinder, a first piston provided in the cylinder so as to be movable in an axial direction of the cylinder, a first piston, A first piston coupled to the piston in a state of being spaced apart in the axial direction, and provided in the cylinder so as to be movable in the axial direction, wherein the first piston is partitioned in the cylinder by the first piston; A first fluid chamber located on one side of the axial direction from the piston, a second fluid chamber defined by the first and second pistons and between the first and second pistons, and a second piston. And at least a third fluid chamber located on the other side of the second piston in the axial direction, the working fluid filled in the first to third fluid chambers, and the first and second fluid chambers. Between the first fluid chamber and the second fluid chamber. A first communication path for flowing the working fluid, and a second communication path communicating with the second and third fluid chambers and for flowing the working fluid between the second fluid chamber and the third fluid chamber. It is further provided with the feature.

  In the fluid damper having the above-described configuration, the first and second pistons are provided in the cylinder so as to be movable in the axial direction, and the first and second pistons are connected in a state of being spaced apart from each other in the axial direction. ing. Further, in the cylinder, a first fluid chamber defined by the first piston, located on one side in the axial direction of the first piston, and a first and second piston defined by the first and second pistons. A second fluid chamber between the two pistons and a third fluid chamber defined by the second piston and located on the other side in the axial direction with respect to the second piston are provided at least. Further, the first to third fluid chambers are filled with the working fluid, and the first communication path for causing the working fluid to flow between the first fluid chamber and the second fluid chamber is the first and second fluid chambers. A second communication path that communicates with the fluid chamber and allows the working fluid to flow between the second fluid chamber and the third fluid chamber communicates with the second and third fluid chambers.

  In the fluid damper having the above-described configuration, the first and second pistons move to one side in the axial direction with respect to the cylinder by inputting external force due to vibration to the cylinder, the first piston, and the second piston. When this is done, the working fluid in the first fluid chamber is pressed by the first piston, a part of the pressed working fluid flows through the first communication passage, the pressure is released to the second fluid chamber side, and The working fluid in the two fluid chambers is pressed by the second piston, and a part of the pressed working fluid flows through the second communication passage, and the pressure is released to the third fluid chamber side. On the other hand, when the first and second pistons move to the other side in the axial direction with respect to the cylinder, the working fluid in the third fluid chamber is pressed by the second piston, and the pressed working fluid A part flows in the second communication passage, and the pressure is released to the second fluid chamber side, the working fluid in the second fluid chamber is pressed by the first piston, and a part of the pressed working fluid is The first fluid passage flows and the pressure is released to the first fluid chamber side.

  As apparent from the above operation, when an external force due to vibration is input to the cylinder or the like, the viscous resistance force of the working fluid can be applied to both the first and second pistons. A larger damping force according to the pressure receiving area of the two pistons can be obtained. In addition, unlike the conventional fluid damper described above, no partition wall is provided between the first piston and the second piston in the cylinder. Therefore, when assembling the fluid damper, the cylinder is complicatedly divided in the radial direction. Assembling work can be easily performed without preparing a pair of divided cylinders or providing a seal with a special shape on the entire joint surface of the pair of divided cylinders.

  The invention according to claim 2 is the fluid damper according to claim 1, wherein the first piston is provided in the cylinder so as to be movable in the axial direction in the first predetermined section, and the second piston is provided in the cylinder. In the second predetermined section aligned with the first predetermined section in the axial direction, the second predetermined passage is provided so as to be movable in the axial direction. The second communication path includes a plurality of communication paths. The moving fluid is configured to flow between the second fluid chamber and the third fluid chamber when moving in a plurality of predetermined sections in the predetermined section.

  According to this configuration, the first piston is movable in the axial direction in the first predetermined section in the cylinder, and the second piston is movable in the axial direction in the second predetermined section aligned with the first predetermined section in the cylinder in the axial direction. Is provided. Further, the second communication path is constituted by a plurality of communication paths, and the plurality of communication paths are used when the second piston moves in a plurality of different predetermined sections in the second predetermined section, respectively. The working fluid is configured to flow between the second fluid chamber and the third fluid chamber. As described above, when the second piston is moving in each of the plurality of predetermined sections, the damping force of the fluid damper is made to move to the moving position of the second piston by causing the working fluid to flow in the corresponding communication path. It can be changed accordingly. Note that the plurality of predetermined sections may partially or entirely overlap each other, or may not overlap.

  According to a third aspect of the present invention, in the fluid damper according to the second aspect, the first communication passage bypasses the first piston, and the first fluid chamber and a portion in the first predetermined section in the second fluid chamber. A rotary mass that is rotatable, and a power conversion mechanism that is provided in the first communication path, converts the flow of the working fluid in the first communication path into a rotational motion, and transmits the rotational motion to the rotary mass; Is further provided.

  According to this configuration, the first communication path bypasses the first piston, and is configured to communicate with the first fluid chamber and the portion in the first predetermined section of the second fluid chamber, The single communication path is provided with a power conversion mechanism that converts the flow of the working fluid in the first communication path into a rotational motion and transmits the rotational motion to a rotatable rotary mass. As a result, as the working fluid flows through the first communication passage, in addition to the viscous resistance force due to the working fluid, a rotational inertia effect due to the rotating mass can be further obtained, so that a larger damping force of the fluid damper can be obtained. it can.

  According to a fourth aspect of the present invention, in the fluid damper according to the second or third aspect, one of the plurality of communication passages includes a third predetermined section in which the second piston is located inside the second predetermined section in the axial direction. While moving, the second piston is bypassed, and the second fluid chamber is configured as a bypass passage that allows the working fluid to flow between a portion in the second predetermined section and the third fluid chamber, and includes a plurality of communication channels. Of the passages, the communication passages other than the bypass passage include a first communication hole and a second communication hole formed so as to penetrate the second piston in the axial direction. The first communication hole is closed when the difference between the pressure of the working fluid in the two fluid chambers and the pressure of the working fluid in the third fluid chamber is smaller than the first predetermined value, and the first communication hole is reached when the first predetermined value is reached. A first pressure regulating valve that opens the communication hole is provided; The through hole closes the second communication hole when the difference between the pressure of the working fluid in the third fluid chamber and the pressure of the working fluid in the second fluid chamber is smaller than the second predetermined value, and sets the second predetermined value to A second pressure regulating valve is provided that opens the second communication hole when the second communication hole is reached.

  According to this configuration, one of the plurality of communication passages bypasses the second piston when the second piston is moving in the third predetermined section located inside the second predetermined section in the axial direction. The second fluid chamber is configured as a bypass passage for allowing the working fluid to flow between a portion in the second predetermined section and the third fluid chamber, and a communication passage other than the bypass passage among the plurality of communication passages is formed. Includes a first communication hole and a second communication hole formed so as to penetrate the second piston in the axial direction. The first communication hole closes the first communication hole when the difference between the pressure of the working fluid in the second fluid chamber and the pressure of the working fluid in the third fluid chamber is smaller than the first predetermined value, 1 A first pressure regulating valve that opens the first communication hole when a predetermined value is reached is provided, and the second communication hole has a pressure of the working fluid in the third fluid chamber and a working fluid in the second fluid chamber. A second pressure regulating valve is provided that closes the second communication hole when the difference from the pressure is smaller than the second predetermined value and opens the second communication hole when the second predetermined value is reached.

  With the above configuration, in the fluid damper, when the second piston moves in the third predetermined section on the inner side in the second predetermined section, the working fluid passes through the bypass passage between the second fluid chamber and the third fluid chamber. Flow between. Further, when the second piston is positioned in both outer axial sections (hereinafter referred to as “predetermined outer section”) in the second predetermined section than the third predetermined section, the working fluid does not flow in the bypass passage. When the pressure difference between the working fluids in the second and third fluid chambers reaches the first or second predetermined value due to the action of an external force on the second piston, the first or second pressure regulating valve causes the first or second pressure regulating valve to As a result of opening the communication hole, the fluid flows between the second fluid chamber and the third fluid chamber through the first or second communication hole, and the second piston moves in the predetermined outer section. As described above, when the second piston moves in the inner third predetermined section, a smaller damping force of the fluid damper can be obtained, and when the second piston moves in the predetermined outer section, the fluid damper A larger damping force can be obtained.

It is sectional drawing which shows the fluid damper by 1st Embodiment of this invention. It is sectional drawing which follows the II-II line of FIG. It is a block diagram which shows the control apparatus of the fluid damper of FIG. It is a figure which shows roughly the fluid damper of FIG. 1 with a part of building which applied this. It is sectional drawing which shows the fluid damper by 2nd Embodiment of this invention. It is a block diagram which shows the control apparatus of the fluid damper of FIG. It is sectional drawing which shows the fluid damper by 3rd Embodiment of this invention. It is sectional drawing which shows the fluid damper by 4th Embodiment of this invention. 8 is a cross-sectional view illustrating the fluid damper in FIG. 8 when (a) the first and second pistons move to the first side wall, and (b) when the first and second pistons move to the second side wall, respectively. FIG. It is sectional drawing which shows the fluid damper by 5th Embodiment of this invention. It is a block diagram which shows the control apparatus of the fluid damper of FIG. It is sectional drawing which shows the fluid damper by 6th Embodiment of this invention. It is sectional drawing which shows the fluid damper by 7th Embodiment of this invention. It is a figure which shows the modification of the some communication path as a 2nd communication path.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 shows a fluid damper 1 according to a first embodiment of the present invention. The fluid damper 1 is configured as a so-called active damper, and includes a cylinder 2, a first piston 3, a second piston 4 and a piston rod 5 provided in the cylinder 2, as shown in FIG. The cylinder 2 includes a cylindrical peripheral wall 2a, and disk-shaped first side walls 2b and second side walls 2c provided concentrically and integrally at one end and the other end in the axial direction of the peripheral wall 2a. ing. A first attachment FL1 is provided on the first side wall 2b via a universal joint. Further, a rod guide hole 2d penetrating in the axial direction is formed in the second side wall 2c, and the piston rod 5 is inserted into the rod guide hole 2d via a ring-shaped seal. The piston rod 5 extends in the axial direction of the cylinder 2, protrudes outward from the second side wall 2 c, and is movable in the axial direction with respect to the cylinder 2.

  The first and second pistons 3 and 4 are formed in a columnar shape, the first piston 3 is at one end of the piston rod 5 in the axial direction, the second piston 4 is at the center of the piston rod 5 in the axial direction, Each is provided concentrically and integrally. A ring-shaped seal is provided on the outer periphery of each of the first and second pistons 3 and 4. In the cylinder 2, a first fluid chamber 2e is defined by the peripheral wall 2a, the first side wall 2b, and the first piston 3, and the second fluid chamber is defined by the peripheral wall 2a, the first and second pistons 3, 4. 2f is defined, and the third fluid chamber 2g is defined by the peripheral wall 2a, the second piston 4, and the second side wall 2c. The first to third fluid chambers 2e to 2g are filled with a working fluid HF, and the working fluid HF is made of, for example, silicon oil.

  The first piston 3 is slidable in the axial direction of the cylinder 2 in a predetermined first piston section DP1 in the cylinder 2. The first piston section DP1 is in the first predetermined section D1 on the first side wall 2b side, and includes a communication portion of a first communication path 10 and a first fluid chamber 2e, which will be described later, a first communication path 10 and a second communication path. It is set in a section between the fluid chamber 2f and the communicating portion. The second piston 4 is provided to be slidable in the axial direction of the cylinder 2 in a predetermined second piston section DP <b> 2 in the cylinder 2. The second piston section DP2 is in a second predetermined section D2 on the second side wall 2c side in the cylinder 2, and is connected to a communication portion between a second communication path 11 and a second fluid chamber 2f, which will be described later, and a second communication path. 11 and a section between the communication portion of the third fluid chamber 2g. Further, a second attachment FL2 is provided at the other end of the piston rod 5 via a universal joint. The first and second predetermined sections D1 and D2 are arranged so as not to overlap each other in the axial direction.

  Further, the first piston 3 is formed with a plurality of first communication holes 3a and second communication holes 3b (only one of which is shown) penetrating in the axial direction, and the first and second communication holes 3a, 3b. Are provided with a first pressure regulating valve 6 and a second pressure regulating valve 7, respectively. The first pressure regulating valve 6 includes a valve body and a spring that biases the valve body in the valve closing direction. The valve body is moved in the valve opening direction by the positive pressure of the working fluid HF in the first fluid chamber 2e. The second fluid chamber 2f is configured to be pressed in the valve closing direction by the positive pressure of the working fluid HF in the second fluid chamber 2f. Further, when the difference between the pressure of the working fluid HF in the first fluid chamber 2e and the pressure of the working fluid HF in the second fluid chamber 2f is smaller than a predetermined value, the first pressure regulating valve 6 has the first communication hole 3a. When the predetermined value is reached, the first communication hole 3a is opened. When the first communication hole 3a is opened by the first pressure regulating valve 6, the first and second fluid chambers 2e and 2f communicate with each other through the first communication hole 3a.

  Similar to the first pressure regulating valve 6, the second pressure regulating valve 7 is configured by a valve body and a spring that urges the valve body in a valve closing direction, and this valve body serves as a working fluid HF in the second fluid chamber 2f. The positive pressure is configured to be pressed in the valve opening direction, and the positive pressure of the working fluid HF in the first fluid chamber 2e is pressed in the valve closing direction. Further, when the difference between the pressure of the working fluid HF in the second fluid chamber 2f and the pressure of the working fluid HF in the first fluid chamber 2e is smaller than the predetermined value, the second pressure regulating valve 7 is connected to the second communication valve 7f. When the hole 3b is closed and reaches a predetermined value, the second communication hole 3b is opened. When the second communication hole 3b is opened by the second pressure regulating valve 7, the second and first fluid chambers 2f and 2e communicate with each other through the second communication hole 3b.

  Further, like the third piston 3, the second piston 4 has a plurality of first communication holes 4a and second communication holes 4b (only one of which is shown) penetrating in the axial direction. A first pressure regulating valve 8 and a second pressure regulating valve 9 are provided in the second communication holes 4a and 4b, respectively. The first pressure regulating valve 8 includes a valve body and a spring that urges the valve body in the valve closing direction, like the first pressure regulating valve 6 of the first piston 3, and this valve body is formed in the second fluid chamber 2f. The positive pressure of the working fluid HF is pressed in the valve opening direction, and the positive pressure of the working fluid HF in the third fluid chamber 2g is pressed in the valve closing direction. Further, when the difference between the pressure of the working fluid HF in the second fluid chamber 2f and the pressure of the working fluid HF in the third fluid chamber 2g is smaller than the predetermined value, the first pressure regulating valve 8 When the hole 4a is closed and reaches a predetermined value, the first communication hole 4a is opened. When the first communication hole 4a is opened by the first pressure regulating valve 8, the second and third fluid chambers 2f and 2g communicate with each other through the first communication hole 4a.

  Similar to the first pressure regulating valve 8, the second pressure regulating valve 9 is composed of a valve body and a spring that urges the valve body in the valve closing direction, and this valve body is used for the working fluid HF in the third fluid chamber 2g. The positive pressure is configured to be pressed in the valve opening direction, and the positive pressure of the working fluid HF in the second fluid chamber 2f is pressed in the valve closing direction. Further, when the difference between the pressure of the working fluid HF in the third fluid chamber 2g and the pressure of the working fluid HF in the second fluid chamber 2f is smaller than the predetermined value, the second pressure regulating valve 9 When the hole 4b is closed and reaches a predetermined value, the second communication hole 4b is opened. When the second communication hole 4b is opened by the second pressure regulating valve 9, the third and second fluid chambers 2g and 2f communicate with each other through the second communication hole 4b.

  The first and second pressure regulating valves 6 to 9 having the above configuration prevent the pressure of the working fluid HF from becoming excessive in the first to third fluid chambers 2e to 2g, and consequently the axial force (axial direction of the fluid damper 1). An excessive force) is prevented. In addition, although the differential pressure | voltage of the working fluid HF which the 1st and 2nd pressure regulation valves 6-9 open is set to the mutually same predetermined value, you may set to a mutually different value.

  The fluid damper 1 further includes a first communication path 10 and a second communication path 11 connected to the cylinder 2. The first communication passage 10 is configured to bypass the first piston 3 and communicate with the first fluid chamber 2e and a portion of the second fluid chamber 2f in the first predetermined section D1, The passage 11 is configured to bypass the second piston 4 and communicate with a portion of the second fluid chamber 2f in the second predetermined section D2 and the third fluid chamber 2g. The cross-sectional area of the first and second communication passages 10 and 11 is set to a value smaller than the cross-sectional area of the cylinder 2, and the first and second communication holes 3a of the first and second pistons 3 and 4 are set. It is set to a value larger than the cross-sectional area of 3b, 4a, 4b. Further, the first and second communication passages 10 and 11 are filled with a working fluid HF.

  The fluid damper 1 also adjusts the pressure of the working fluid HF in the first and second fluid chambers 2e and 2f by changing the flow amount of the working fluid HF in the first communication passage 10. Is further provided. The first fluid pressure adjusting device 12 has a gear pump that uses the first electric motor 13 as a power source. The gear pump is of a circumscribed gear type and includes a casing 14, a first gear 15 and a second gear 16 accommodated in the casing 14, and the like. The casing 14 is integrally provided at the center of the first communication path 10, and the inside thereof communicates with the first communication path 10 through two entrances 14 a and 14 a that face each other.

  The first gear 15 is a spur gear and is provided integrally with the first rotating shaft 17. The first rotating shaft 17 extends horizontally in a direction orthogonal to the first communication path 10, is rotatably supported by the casing 14, and slightly protrudes outside the casing 14 (see FIG. 2). Similar to the first gear 15, the second gear 16 is configured by a spur gear, is provided integrally with the second rotating shaft 18, and meshes with the first gear 15. The second rotating shaft 18 extends in parallel with the first rotating shaft 17 and is rotatably supported by the casing 14. Further, the meshing portions of the first and second gears 15 and 16 face the entrances 14 a and 14 a of the casing 14.

  The first electric motor 13 is, for example, a DC motor capable of generating electric power, and a rotor (not shown) of the first electric motor 13 is concentrically connected to the first rotating shaft 17, and the first gear 15 and the first rotating shaft. 17 and can rotate together. As shown in FIG. 3, the first electric motor 13 is connected to a power source 22 that is a battery via a control device 21. The control device 21 is configured by a combination of a rectifier, a CPU, a RAM, a ROM, an I / O interface, and the like.

  For example, as shown in FIG. 4, the fluid damper 1 having the above-described configuration has a V V at a joint portion between the upper beam BU and the left column PL of the building B and a joint portion between the upper beam BU and the right column PR of the building B. It is connected via a brace material BR in the shape of a character, and is connected to a joint portion of the lower beam BD of the building B and the right column PR via a connecting member EN. In this case, the first fixture FL1 is attached to the lower end of the brace material BR, the second fixture FL2 is attached to the connecting member EN, and the fluid damper 1 extends in the left-right direction. The brace material BR and the connecting member EN are made of, for example, H-shaped steel. When the building B is not vibrating, the first and second pistons 3 and 4 are in the neutral position shown in FIG. In addition, in FIG. 4, illustration of the 1st and 2nd communicating paths 10 and 11 is abbreviate | omitted for convenience.

  Further, in the fluid damper 1, when a relative displacement occurs in the left-right direction between the upper and lower beams BU and BD due to vibration of the building B, the relative displacement is transmitted as an external force to the cylinder 2 and the piston rod 5. The rod 5 moves in the axial direction relative to the cylinder 2, and the first and second pistons 3 and 4 integral with the piston rod 5 slide in the cylinder 2 in the axial direction. In this case, when the first and second pistons 3 and 4 slide toward the first side wall 2b of the cylinder 2 (when the fluid damper 1 contracts), the working fluid HF in the first fluid chamber 2e is the first. While being pressed by the piston 3, a part of the fluid flows to the second fluid chamber 2f side through the first communication passage 10, and the working fluid HF in the second predetermined section D2 in the second fluid chamber 2f is Pressed by the second piston 4, a part of which flows through the second communication passage 11 to the third fluid chamber 2 g side.

  On the contrary, when the first and second pistons 3 and 4 slide toward the second side wall 2c of the cylinder 2 (when the fluid damper 1 extends), the working fluid HF in the third fluid chamber 2g. Is pressed by the second piston 4 and part of the fluid flows to the second fluid chamber 2f side through the second communication passage 11, and the working fluid in a portion in the first predetermined section D1 in the second fluid chamber 2f. HF is pressed by the first piston 3, and a part of the HF flows through the first communication passage 10 to the first fluid chamber 2 e side.

  As is clear from the above operation, during the vibration of the building B, the pressure of the working fluid HF in the first to third fluid chambers 2e to 2g resists the external force transmitted to the cylinder 2 and the piston rod 5 as described above. That is, it acts on the building B as a damping force for suppressing the vibration of the building B. In the fluid damper 1, during the vibration of the building B, the damping force is adjusted by controlling the first electric motor 13, and the first to third control modes are set as the control modes. In these first and second control modes, the electric power from the power source 22 is supplied to the first electric motor 13, and the first gear 15 is rotated by the first electric motor 13, thereby operating in the first communication path 10. By causing the fluid HF to flow, the damping force of the fluid damper 1 is adjusted.

  More specifically, in the first control mode, it is generated by driving the first gear 15 by the first electric motor 13 when an external force due to vibration is transmitted to the piston rod 5, the first and second pistons 3, 4. The direction of flow of the working fluid HF (hereinafter referred to as “gear-driven flow direction”) is opposite to the direction of flow of the working fluid HF (hereinafter referred to as “vibration flow direction”) generated by the movement of the first piston 3 due to external force due to vibration. Thus, the rotation direction of the first electric motor 13 is controlled. Thereby, a larger damping force of the fluid damper 1 is generated. In this case, the damping force of the fluid damper 1 is adjusted by changing the rotation speed of the first electric motor 13, and the working fluid HF that flows in the direction opposite to the vibration flow direction as the rotation speed of the first electric motor 13 increases. As the amount of flow increases, the damping force increases.

  In the second control mode, the first electric motor is arranged such that the gear drive flow direction is the same as the vibration flow direction when an external force due to vibration is transmitted to the piston rod 5 and the first and second pistons 3 and 4. 13 rotation directions are controlled. Thereby, a smaller damping force of the fluid damper 1 is generated. Also in this case, the damping force of the fluid damper 1 is adjusted by changing the rotation speed of the first electric motor 13, and unlike the case of the first control mode, the higher the rotation speed of the first electric motor 13, The damping force becomes smaller as the flow amount of the working fluid HF flowing in the same direction as the vibration flow direction increases.

  In the third control mode, the first electric motor 13 generates power using the flow of the working fluid HF generated by the movement of the first piston 3 due to the external force due to vibration, and the generated power is changed. The damping force of the fluid damper 1 is adjusted. In this case, the flow of the working fluid HF is converted into rotational motion by the first gear 15 and further converted (electric power generation) into electric energy by the first electric motor 13. The damping force of the fluid damper 1 in the third control mode is greater because the working fluid HF is less likely to flow as the power generated by the first electric motor 13 increases. The magnitude relationship of the damping force obtained in each of the first to third control modes is in the order of first control mode> third control mode> second control mode. Note that one or two of the first to third control modes may be set as the control mode. Further, the power generated by the first electric motor 13 is charged to the power source 22.

  When the building B vibrates due to an earthquake or the like, the control device 21 accelerates acceleration due to vibration of the upper beam BU (hereinafter referred to as “upper beam vibration acceleration”) and acceleration due to vibration of the ACBU and lower beam BD (hereinafter referred to as “lower beam vibration acceleration”). In accordance with the ACBD, the vibration suppression control process for executing the control in the first to third control modes is executed in order to suppress the vibration of the building B in accordance with the control program stored in the ROM. These upper beam vibration acceleration ACBU and lower beam vibration acceleration ACBD are detected by, for example, semiconductor-type first and second acceleration sensors 23 and 24, and their detection signals are output to the control device 21.

  In this processing, first, the lower beam vibration acceleration ACBD is integrated twice to calculate the displacement due to the vibration of the lower beam BD (hereinafter referred to as “lower beam vibration displacement DIBD”), and the upper beam vibration acceleration ACBU is calculated twice. By integrating, a displacement due to vibration of the upper beam BU (hereinafter referred to as “upper beam vibration displacement DIBU”) is calculated. The lower beam vibration displacement DIBD and the upper beam vibration displacement DIBU are displacements of the lower beam BD and the upper beam BU with respect to the absolute coordinate system, respectively.

  Next, a deviation between the calculated upper beam vibration displacement DIBU and lower beam vibration displacement DIBD is calculated as an inter-beam vibration displacement DIUD. Next, a feedback control term FBC is calculated by multiplying the calculated inter-beam vibration displacement DIUD by a predetermined feedback coefficient FK. Next, a control signal SC for controlling the first electric motor 13 is calculated by adding a predetermined feedforward control term FFC to the calculated feedback control term FBC. In the vibration suppression control process, during the vibration of the building B, the above calculation operation is repeatedly executed at a predetermined control cycle.

  The control signal SC corresponds to a target value for the displacement of the first piston 3 with respect to the cylinder 2. When the control signal SC is calculated as described above, one of the first to third control modes described above is selected based on the control signal SC and a predetermined map (not shown) stored in the ROM. Z)), the command value of the power supplied to the first electric motor 13 or the generated power is calculated. Then, by controlling the power supplied to the first electric motor 13 or the generated power based on the calculated command value, the displacement of the first piston 3 is adjusted to the target value represented by the control signal SC. Thus, the damping force of the fluid damper 1 is adjusted.

  In the first embodiment, a so-called proportional term is used as the feedback control term FBC, but an integral term or a differential term may be further used. This is the case with the second to fifth embodiments described later. The same applies to. In this case, the integral term is calculated, for example, by adding a value obtained by multiplying the previous value of the integral term by a predetermined coefficient to the current inter-beam vibration displacement DIUD. The previous value of the integral term is reset to 0 when building B is not vibrating. The differential term is calculated by, for example, multiplying a value obtained by subtracting the previous value of the inter-beam vibration displacement DIUD from the current inter-beam vibration displacement DIUD by a predetermined coefficient.

  Further, in the first embodiment, as is apparent from the above-described calculation method of the control signal SC, the inter-beam vibration displacement DIUD, that is, the deviation between the upper beam vibration displacement DIBU and the lower beam vibration displacement DIBD is 0. 1 The control signal SC for controlling the electric motor 13 is calculated. The control signal is calculated so that the deviation between the vibration speed of the upper beam BU and the vibration speed of the lower beam BD becomes 0. Also good. Also in this case, not only a proportional term but also an integral term or a differential term may be used as a feedback control term used for calculation of a control signal.

  Further, in the fluid damper 1, as is apparent from the above-described configuration, the inertial element composed of the working fluid HF and the first electric motor 13 is connected in series to the elastic element composed of the brace material BR and the connecting member EN. is there. For this reason, the fluid damper 1 functions as an additional vibration system (dynamic vibration absorber) when power is not supplied from the power source 22 to the first electric motor 13 at the time of a power failure in the building B, for example. In this case, the specifications of the additional vibration system are set so that the natural frequency thereof is synchronized with the natural frequency of the building B (for example, the natural frequency of the primary mode). The setting is performed based on, for example, fixed point theory. Here, the natural frequency of the additional vibration system includes the inertial mass mF due to the flow of the working fluid HF, the rotational inertial mass mM of the first electric motor 13 considering the influence of the gear pump of the first fluid pressure adjusting device 12, and the brace. It is determined by the rigidity θT of the material BR or the like (= sqrt {θT / (mF + mM)} / 2π).

  As described above, in the fluid damper 1 according to the first embodiment, the first piston 3 is provided in the cylinder 2 so as to be slidable in the axial direction in the first predetermined section D1, and the second piston 4 is The first predetermined section D1 and the second predetermined section D2 arranged in the axial direction of the cylinder 2 are slidable in the axial direction. Further, in the cylinder 2, a first fluid chamber 2 e that is defined by the first piston 3 and is located on one side in the axial direction from the first piston 3, and a first and second pistons 3 and 4 are defined. The second fluid chamber 2f between the first and second pistons 3 and 4 and the third fluid chamber defined by the second piston 4 and located on the other side in the axial direction from the second piston 4 2g. Further, the first to third fluid chambers 2e to 2g are filled with the working fluid HF, and the first communication passage for flowing the working fluid HF between the first fluid chamber 2e and the second fluid chamber 2f. 10 communicates with the first and second fluid chambers 2e and 2f, and the second communication passage 11 for allowing the working fluid HF to flow between the second fluid chamber 2f and the third fluid chamber 2g is the second And the third fluid chambers 2f and 2g.

  In the fluid damper 1 having the above configuration, the first and second pistons 3, 4 are moved relative to the cylinder 2 by inputting external force due to vibration to the cylinder 2, the first piston 3, and the second piston 4. When moving to one side in the axial direction, the working fluid HF in the first fluid chamber 2e is pressed by the first piston 3, and the pressed working fluid HF flows through the first communication passage 10 and the pressure is the first. The second fluid chamber 2f escapes and the working fluid HF in the second fluid chamber 2f is pressed by the second piston 4, and the pressed working fluid HF flows through the second communication passage 11 and the pressure is first. It is escaped to the 3 fluid chamber 2g side. On the other hand, when the first and second pistons 3 and 4 move to the other side in the axial direction with respect to the cylinder 2, the working fluid HF in the third fluid chamber 2g is pressed by the second piston 4. The pressed working fluid HF flows through the second communication passage 11, the pressure is released to the second fluid chamber 2 f side, and the working fluid HF in the second fluid chamber 2 f is pressed by the first piston 3. The pressed working fluid HF flows through the first communication passage 10, and the pressure is released to the first fluid chamber 2e side.

  As is clear from the above operation, when an external force due to vibration is input to the cylinder 2 or the like, the viscous resistance force of the working fluid HF can be applied to both the first and second pistons 3 and 4. In addition, a larger damping force can be obtained in accordance with the pressure receiving area of the two pistons including the second pistons 3 and 4. Further, unlike the above-described conventional fluid damper, no partition wall is provided between the first piston 3 and the second piston 4 in the cylinder 2, so that assembling work is easily performed as described below. be able to.

  The fluid damper 1 is assembled as follows, for example. That is, first, the peripheral wall 2a and the first side wall 2b are integrally formed by casting or the like, and the first fixture FL1 is attached to the first side wall 2b. In this case, a communication hole for connecting the first and second communication passages 10 and 11 is formed in the peripheral wall 2a. Next, the first and second pistons 3 and 4 are attached to the piston rod 5, and the three members 3 to 5 are accommodated in the cylinder 2. Next, the piston rod 5 is inserted into the rod guide hole 2d of the second side wall 2c via a ring-shaped seal, and in this state, the second side wall 2c is inserted via a ring-shaped seal (not shown). It is attached to the peripheral wall 2a. Next, the second fixture FL <b> 2 is attached to the piston rod 5. Next, the first communication path 10 provided with the first fluid pressure adjusting device 12 and the second communication path 11 are connected to the peripheral wall 2a via a ring-shaped seal (not shown).

  As described above, in assembling the fluid damper 1, it is only necessary to provide a general ring-shaped seal between the peripheral wall 2a, the second side wall 2c, the first and second communication passages 10, 11, and the cylinder. Assembling work is easy without preparing a pair of split cylinders of complicated shape divided in the radial direction as 2 or providing a specially shaped seal on the entire joint surface of the pair of split cylinders. It can be carried out.

  Further, since the pressure of the working fluid HF in the first and second fluid chambers 2e and 2f is adjusted by the fluid pressure adjusting device 12 so as to move the first and second pistons 3 and 4 in the cylinder 2, The fluid damper 1 according to the invention can function as a so-called active fluid damper.

  Further, the first communication passage 10 is configured to bypass the first piston 3 and to communicate with the first fluid chamber 2e and a portion in the first predetermined section D1 in the second fluid chamber 2f. The fluid pressure adjusting device 12 is provided in the first communication passage 10 and changes the flow amount of the working fluid HF in the first communication passage 10 to change the pressure of the working fluid HF in the first and second fluid chambers 2e and 2f. Configured to adjust. Thus, since the fluid pressure adjusting device 12 provided in the first communication passage 10 is used to adjust the pressure of the working fluid HF in the first and second fluid chambers 2e, 2f, the first and second fluid chambers are used. Compared to the case where the pressure adjusting fluid pumps are individually connected to 2e and 2f, the entire fluid damper 1 can be reduced in size.

  Next, a fluid damper 31 according to a second embodiment of the present invention will be described with reference to FIGS. 5 and 6. The fluid damper 31 is mainly different from the first embodiment in that a second fluid pressure adjusting device 32 is provided in the second communication path 11. In FIG.5 and FIG.6, the same code | symbol is attached | subjected about the same component as 1st Embodiment. Hereinafter, a description will be given focusing on differences from the first embodiment.

  The second fluid pressure adjusting device 32 shown in FIG. 5 adjusts the pressure of the working fluid HF in the second and third fluid chambers 2f and 2g by changing the flow amount of the working fluid HF in the second communication passage 11. And is configured in the same manner as the first fluid pressure adjusting device 12. Specifically, the second fluid pressure adjusting device 32 has a gear pump using the second electric motor 33 as a power source. The gear pump is of a circumscribed gear type, and includes a casing 34, a first gear 35 and a second gear 36 accommodated in the casing 34, and the like. The casing 34 is integrally provided in the central portion of the second communication path 11, and the inside thereof communicates with the second communication path 11 through two entrances 34 a and 34 a facing each other.

  The first gear 35 is a spur gear and is integrally provided on the first rotating shaft 37. The first rotating shaft 37 extends horizontally in a direction orthogonal to the second communication path 11, is rotatably supported by the casing 34, and slightly protrudes outside the casing 34. Similar to the first gear 35, the second gear 36 is configured by a spur gear, is provided integrally with the second rotating shaft 38, and meshes with the first gear 35. The second rotating shaft 38 extends in parallel with the first rotating shaft 37 and is rotatably supported by the casing 34. Further, the meshing portions of the first and second gears 35 and 36 face the entrances 34 a and 34 a of the casing 34.

  The control device 41 according to the second embodiment is connected to the second electric motor 33 in addition to the first electric motor 13, the power source 22, and the first and second acceleration sensors 23 and 24 described above. A separate electric circuit for controlling the electric motors 13 and 33 is provided. In addition to the first electric motor 13, the control device 41 controls the second electric motor 33 in the first to third control modes (vibration suppression control processing) described above. In this case, basically, the damping force of the fluid damper 31 is changed by the control of the first electric motor 13, and the output torque (including positive torque and negative torque) of the second electric motor 33 is 0. When a smaller or larger damping force is required, the second electric motor 33 in addition to the first electric motor 13 is controlled in the first to third control modes. Further, in the fluid damper 31, a fourth control mode is set as a control mode for controlling the first and second electric motors 13 and 33.

  In the fourth control mode, during the vibration of the building B (see FIG. 4), power is generated by one of the first and second electric motors 13 and 33 using the flow of the working fluid HF, and the generated power is The other one of the first and second electric motors 13 and 33 is supplied. Of the first and second electric motors 13 and 33, the motor to which the generated power is supplied is controlled such that the rotation direction of the gear is the same as or opposite to the direction of vibration flow. During the fourth control mode, the generated power of one of the first and second electric motors 13 and 33 is controlled to a predetermined constant value, and the first and second electric motors 13 and 33 to which the generated power is supplied. The other is controlled by the vibration suppression control process described above. In this case, when the generated power is surplus, the surplus is charged in the power source 22, and when the generated power is deficient, the deficit is supplemented by the power of the power source 22.

  Note that during the fourth control mode, when power cannot be transferred between the power source 22 and the first and second electric motors 13 and 33 due to disconnection or failure of the power source 22, the first and second electric motors are used. The generated power of one of the motors 13 and 33 is supplied to the other as it is.

  As described above, according to the second embodiment, in addition to the first fluid pressure adjusting device 12 that adjusts the pressure of the working fluid HF in the first and second fluid chambers 2e, 2f, the second and third fluid chambers 2f. Since the second fluid pressure adjusting device 32 that adjusts the pressure of the working fluid HF at 2 g is provided, the change range of the damping force of the fluid damper 31 can be increased. In addition, the above-described effects according to the first embodiment, that is, the effect that the fluid damper 31 can be easily assembled can be obtained in the same manner.

  Next, a fluid damper 51 according to a third embodiment of the present invention will be described with reference to FIG. The fluid damper 51 is mainly different from the first embodiment in that it further includes a gear motor 52 provided in the second communication path 11 and a rotatable rotating mass 53. In FIG. 7, the same components as those in the first embodiment are denoted by the same reference numerals. Hereinafter, a description will be given focusing on differences from the first embodiment.

  As with the gear pump of the first fluid pressure adjusting device 12, the gear motor 52 includes a casing 54, a first gear 55 and a second gear 56 that are housed in the casing 54 and are formed of spur gears. The casing 54 is integrally provided in the central portion of the second communication path 11, and the inside thereof communicates with the second communication path 11 via two entrances 54 a and 54 a facing each other.

  Further, the first gear 55 is provided integrally with the first rotating shaft 57. The first rotating shaft 57 extends horizontally in a direction orthogonal to the second communication path 11, is rotatably supported by the casing 54, and slightly protrudes outside the casing 54. The second gear 56 is provided integrally with the second rotation shaft 58 and meshes with the first gear 55. The second rotating shaft 58 extends in parallel with the first rotating shaft 57 and is rotatably supported by the casing 54. Further, the meshing portions of the first and second gears 55 and 56 face the entrances 54 a and 54 a of the casing 54.

  The rotary mass 53 is made of a material having a relatively large specific gravity, for example, a disk made of iron. The rotating mass 53 is concentrically attached to the first rotating shaft 57 and rotates integrally with the first gear 55 and the first rotating shaft 57.

  In the fluid damper 51 having the above configuration, the working fluid HF that has flowed into the casing 54 when the working fluid HF flows through the second communication passage 11 as described above with vibration of the building B (see FIG. 4). Thus, the first and second gears 55 and 56 are rotationally driven, and the rotary mass 53 integrated with the first gear 55 rotates.

  As described above, according to the third embodiment, the flow of the working fluid HF is converted into rotational motion by the gear motor 52, and the rotating mass 53 is rotated, so that the damping force of the working fluid HF according to the first embodiment is increased. Since the rotary inertia effect by the rotary mass 53 is added, a larger damping force of the fluid damper 51 can be obtained.

  Further, in the fluid damper 51, an inertia element composed of the rotating mass 53 is added in parallel to the inertia element composed of the working fluid HF. Therefore, in this case, the specifications for determining the natural frequency of the additional vibration system include the volume efficiency of the gear motor 52 and the mass and diameter of the rotating mass 53 in addition to the above-described specifications in the first embodiment. included. Therefore, by appropriately setting these specifications, the natural frequency of the additional vibration system can be tuned to the primary natural frequency of the building B. In addition, the above-described effects according to the first embodiment, that is, the effect that the fluid damper 51 can be easily assembled can be obtained in the same manner.

  Next, a fluid damper 61 according to a fourth embodiment of the present invention will be described with reference to FIGS. The fluid damper 61 is mainly different from the first and third embodiments in the configuration of the second communication passage 62. 8 and 9, the same components as those in the first and third embodiments are denoted by the same reference numerals. The following description will focus on differences from the first and third embodiments.

  The second communication passage 62 is configured to bypass the second piston 4 and communicate with the second and third fluid chambers 2f and 2g when the second piston 4 is in the third predetermined section D3 in the cylinder 2. Has been. The third predetermined section D3 is set as an inner section in the above-described second piston section DP2, which is a sliding section of the second piston 4, and both sides in the axial direction centering on the neutral position of the second piston 4 Are extended with the same length. In addition, you may set the 3rd predetermined area D3 so that it may extend in mutually different length to the both sides of an axial direction centering | focusing on the neutral position of the 2nd piston 4. FIG.

  Further, the casing 54 of the gear motor 52 described above is integrally provided at the center of the second communication passage 62.

  In the fluid damper 61 having the above configuration, when the second piston 4 slides in the third predetermined section D3 due to the vibration of the building B (see FIG. 4), the working fluid HF pressed by the second piston 4 Flows between the second fluid chamber 2f and the third fluid chamber 2g via the second communication passage 62 as in the first embodiment. Accordingly, as described in the third embodiment, the flow of the working fluid HF in the second communication passage 62 is transmitted to the rotary mass 53 in a state of being converted into the rotary motion, whereby the rotary mass 53 rotates, A rotational inertia effect by the rotational mass 53 is given.

  Further, as shown in FIGS. 9A and 9B, the second piston 4 is moved by the input of an external force in the axially opposite outer sections (hereinafter referred to as “predetermined”) in the second piston section DP2. The working fluid HF pressed by the second piston 4 stops flowing in the second communication passage 62, and the first or second pressure regulating valves 8, 9 are opened. Accordingly, the first piston 2 flows through the first or second communication holes 4a, 4b, and the second piston 4 slides in the predetermined outer section DO. In this case, when an external force that causes the second piston 4 to slide the predetermined outer section DO toward the first side wall 2b is input, the pressure of the working fluid HF in the second fluid chamber 2f and the third fluid chamber When the difference from the pressure of the working fluid HF in 2g reaches a predetermined value, the first pressure regulating valve 8 is opened as described above (see FIG. 9A), and the operation in the second fluid chamber 2f is performed. Part of the fluid HF flows to the third fluid chamber 2g through the first communication hole 4a. As a result, a larger viscous damping force of the working fluid HF acts on the second piston 4, so that the damping force of the fluid damper 61 becomes larger.

  On the other hand, when an external force that causes the second piston 4 to slide the predetermined outer section DO toward the second side wall 2c is input, the pressure of the working fluid HF in the third fluid chamber 2g and the second fluid chamber 2f When the difference from the pressure of the working fluid HF inside reaches a predetermined value, the second pressure regulating valve 9 opens as described above (see FIG. 9B), and the working fluid in the third fluid chamber 2g. A part of HF flows to the second fluid chamber 2f through the second communication hole 4b. As a result, a larger viscous damping force of the working fluid HF acts on the second piston 4, so that the damping force of the fluid damper 61 becomes larger.

  As described above, according to the fourth embodiment, when the second piston 4 is moving in the third predetermined section D3 in the second predetermined section D2, the second communication passage 62 is provided with the second fluid chamber 2f. And the third fluid chamber 2g are configured to flow the working fluid HF. Further, when the second piston 4 is positioned in the predetermined outer section DO outside the third predetermined section D3 in the second predetermined section D2, the working fluid HF does not flow through the second communication passage 62, and the second When the pressure difference of the working fluid HF in the second and third fluid chambers 2f, 2g reaches a predetermined value due to the action of external force on the two pistons 4, the first or second pressure regulating valve 8, 9 As a result of the opening of the second communication holes 4a and 4b, the second piston 4 flows through the first or second communication holes 4a and 4b between the second fluid chamber 2f and the third fluid chamber 2g, and the second piston 4 is predetermined. The outer section DO is moved. As described above, when the second piston 4 moves in the inner third predetermined section D3, a smaller damping force of the fluid damper 61 can be obtained, and the second piston 4 moves in the predetermined outer section DO. Sometimes, a larger damping force of the fluid damper 61 can be obtained. In addition, the above-described effects according to the first embodiment, that is, the effect that the fluid damper 61 can be easily assembled can be obtained in the same manner.

  In the fourth embodiment, the first and second communication holes 4a and 4b correspond to a plurality of communication paths in the present invention.

  Next, a fluid damper 71 according to a fifth embodiment of the present invention will be described with reference to FIGS. 10 and 11. The fluid damper 71 is mainly different from the fourth embodiment in that an adjustment valve 72 is provided instead of the gear motor 52. In FIG.10 and FIG.11, the same code | symbol is attached | subjected about the same component as 1st and 4th embodiment. Hereinafter, a description will be given focusing on differences from the first and fourth embodiments.

  The adjustment valve 72 is constituted by, for example, a linear electromagnetic valve, and its opening degree is changed linearly by the control device 81, whereby the flow amount of the working fluid HF in the second communication path 62 changes.

  With the above configuration, according to the fifth embodiment, during the vibration of the building B (see FIG. 4), the opening degree of the adjustment valve 72 is controlled according to the above-described upper beam vibration displacement DIBU and lower beam vibration displacement DIBD. Thus, the range of change on the increasing side of the damping force of the fluid damper 71 can be increased. In addition, the above-described effects according to the first and fourth embodiments, that is, the effect that the fluid damper 31 can be easily assembled can be similarly obtained.

  In the fifth embodiment, as a matter of course, other appropriate valves such as a hydraulically driven on-off valve may be used as the adjustment valve 72.

  Next, a fluid damper 91 according to a sixth embodiment of the present invention will be described with reference to FIG. This fluid damper 91 is configured as a so-called passive damper. Compared with the fourth embodiment, a gear motor 92 and a rotary mass 93 are provided in the first communication path 10 in place of the first fluid pressure adjusting device 12. The difference is mainly in that the gear motor 52 of the second communication passage 62 is omitted. In FIG. 12, the same components as those in the first and fourth embodiments are denoted by the same reference numerals. Hereinafter, a description will be given focusing on differences from the first and fourth embodiments.

  As with the gear motor 52 described in the third embodiment, the gear motor 92 includes a casing 94 and a first gear 95 and a second gear 96 that are housed in the casing 94 and are spur gears. The casing 94 is integrally provided at the center of the first communication path 10, and the inside thereof communicates with the first communication path 10 via two entrances 94 a and 94 a facing each other.

  Further, the first gear 95 is provided integrally with the first rotating shaft 97. The first rotating shaft 97 extends horizontally in a direction orthogonal to the first communication path 10, is rotatably supported by the casing 94, and slightly protrudes from the casing 94. The second gear 96 is provided integrally with the second rotating shaft 98 and meshes with the first gear 95. The second rotation shaft 98 extends in parallel with the first rotation shaft 97 and is rotatably supported by the casing 94. Further, the meshing portions of the first and second gears 95 and 96 face the entrances 94 a and 94 a of the casing 94.

  The rotary mass 93 is made of a material having a relatively large specific gravity, for example, a disc made of iron. The rotating mass 93 is concentrically attached to the first rotating shaft 97 and rotates integrally with the first gear 95 and the first rotating shaft 97.

  In the fluid damper 91 configured as described above, the working fluid HF that has flowed into the casing 94 when the working fluid HF flows through the first communication path 10 as described above with vibration of the building B (see FIG. 4). As a result, the first and second gears 95 and 96 are rotationally driven, and the rotary mass 93 integral with the first gear 95 rotates.

  As described above, according to the sixth embodiment, the flow of the working fluid HF is converted into a rotational motion by the gear motor 92 and the rotating mass 93 is rotated, thereby reducing the damping force of the working fluid HF according to the first embodiment. Since the rotary inertia effect by the rotary mass 93 is added, a larger damping force of the fluid damper 91 can be obtained. In addition, the above-described effects according to the first and fourth embodiments, that is, the effect that the fluid damper 31 can be easily assembled can be similarly obtained.

  In the fluid damper 91, since the inertial element composed of the working fluid HF and the rotating mass 93 is connected in series to the elastic element composed of the brace material BR or the like, the fluid damper 1 is connected to the additional vibration system (dynamic vibration absorption). Function as a container. In this case, the specifications of the additional vibration system are set so that the natural frequency thereof is synchronized with the natural frequency of the building B (for example, the natural frequency of the first-order mode), and the setting is based on, for example, fixed point theory. Done. Here, the natural frequency of the additional vibration system is determined by the inertia mass mF due to the flow of the working fluid HF, the rotary inertia mass mR of the rotary mass 93 considering the influence of the gear motor 92, and the rigidity θT of the brace material BR (= sqrt). {ΘT / (mF + mR)} / 2π).

  Next, a fluid damper 101 according to a seventh embodiment of the present invention will be described with reference to FIG. Similar to the sixth embodiment, the fluid damper 101 is configured as a so-called passive damper. Compared to the sixth embodiment, the fluid damper 101 replaces the first and second communication passages 10 and 62 with the communication grooves 3c and 4c. Are mainly different from each other in that the first and second pistons 3 and 4 are respectively provided. In FIG. 13, the same components as those in the sixth embodiment are denoted by the same reference numerals. Hereinafter, a description will be given centering on differences from the sixth embodiment.

  Each of the communication grooves 3c and 4c is composed of a plurality of grooves extending in the axial direction (only one is shown), the former 3c is in communication with the first and second fluid chambers 2e and 2f, and the latter 4c is It communicates with the second and third fluid chambers 2f, 2g.

  In the fluid damper 101 having the above configuration, when the first and second pistons 3 and 4 slide in the cylinder 2 toward the first side wall 2b in accordance with the vibration of the building B (see FIG. 4), the first fluid The working fluid HF in the chamber 2e is pressed by the first piston 3, and a part thereof flows to the second fluid chamber 2f side through the communication groove 3c, and the working fluid HF in the second fluid chamber 2f is moved to the second piston. 4 and part thereof flows to the third fluid chamber 2g side through the communication groove 4c.

  On the contrary, when the first and second pistons 3 and 4 slide in the cylinder 2 toward the second side wall 2c, the working fluid HF in the third fluid chamber 2g is pressed by the second piston 4, Part of the fluid flows to the second fluid chamber 2f side through the communication groove 4c, and the working fluid HF in the second fluid chamber 2f is pressed by the first piston 3, and part of the fluid passes through the communication groove 3c. It flows to the first fluid chamber 2e side.

  As described above, according to the seventh embodiment, as in the case of the first embodiment, when an external force due to vibration is input to the cylinder 2 or the like, the viscous resistance force of the working fluid HF is changed to the first and second pistons. Since it is made to act on both 3 and 4, the bigger damping force according to the pressure receiving area of the two pistons which consist of the 1st and 2nd pistons 3 and 4 can be obtained. Further, unlike the conventional fluid damper described above, no partition wall is provided between the first piston 3 and the second piston 4 in the cylinder 2, so that the cylinder 2 is arranged in the radial direction when the fluid damper 101 is assembled. Assembling work can be easily performed without preparing a pair of divided cylinders having a complicated shape and providing a special seal on the entire joint surface of the pair of divided cylinders. In the seventh embodiment, unlike the first embodiment, since the first and second communication passages 10 and 11 are not provided, the fluid damper 101 can be more easily assembled accordingly.

  In the seventh embodiment, the first and second pistons 3 and 4 may be provided with communication holes penetrating in the axial direction instead of the communication grooves 3c and 4c. Alternatively, a communication groove extending in the axial direction may be formed in the peripheral wall 2 a of the cylinder 2, and by setting the outer diameters of the first and second pistons 3 and 4 to be smaller than the inner diameter of the cylinder 2, A communication path may be formed between the cylinder.

  In addition, this invention can be implemented in various aspects, without being limited to the described embodiment. For example, regarding the first embodiment, the first fluid pressure adjusting device 12 is provided in the first communication path 10, but may be provided in the second communication path 11. In addition, regarding the second embodiment, a gear motor 52 and a rotation mass 53 may be provided in the second communication path 11 in addition to the second fluid pressure adjusting device 32. Furthermore, regarding the third and fourth embodiments, an adjustment valve 72 may be provided in the second communication passages 11 and 62 in addition to the gear motor 52 and the rotation mass 53. In addition, in the first, third, fourth, and sixth embodiments, a throttle (orifice) may be provided in the second communication passages 11 and 62. In the fifth embodiment, in place of the adjustment valve 72, a throttle is provided. May be provided.

  Furthermore, regarding the sixth embodiment, a gear motor 52, a rotation mass 53, and an adjustment valve 72 may be provided in the second communication path 62. Moreover, regarding the sixth embodiment, the gear motor 92 and the rotation mass 93 may be omitted.

  Furthermore, regarding the first to sixth embodiments, at least one of the corresponding communication grooves 3c, 4c of the seventh embodiment may be provided in at least one of the first and second pistons 3, 4. Moreover, regarding the fourth to sixth embodiments, when the communication groove 4c is provided in the second piston 4, the communication groove 4c corresponds to a plurality of communication paths in the present invention. In any of these cases, it is needless to say that the above-described variations regarding the communication grooves 3c and 4c may be applied.

  Further, in the first to sixth embodiments, the number of the second communication passages 11 and 62 that bypass the second piston 4 and communicate with the second and third fluid chambers 2f and 2g is one, but two or more. But you can. In this case, the plurality of communication passages as the second communication passages are provided between the second fluid chamber and the third fluid chamber when the second piston moves in the plurality of predetermined sections in the second predetermined section. The working fluid is configured to flow. For example, the fluid damper may be provided with both the second communication passages 11 and 62, and two communication passages PA1 and PA2 as shown in FIG. 14 may be provided as the second communication passage. . As shown in the figure, the communication path PA1 on the first side wall 2b side is changed when the second piston 4 moves in the third predetermined section D3 on the inner side and the predetermined outer section DO on the first side wall 2b side. The cylinder 2 is connected so that the working fluid HF flows between the second fluid chamber 2f and the third fluid chamber 2g. Further, the communication path PA2 on the second side wall 2c side is connected to the second fluid chamber 2f when the second piston 4 is moving in the third predetermined section D3 on the inner side and the predetermined outer section DO on the second side wall 2c side. It is connected to the cylinder 2 so that the working fluid HF flows between the third fluid chambers 2g.

  Moreover, when providing a some communicating path as a 2nd communicating path, in 4th-6th embodiment, predetermined | prescribed outer area DO is set rather than when the 2nd piston 4 is moving inside 3rd predetermined area D3. A plurality of communication passages are configured so that the damping force of the fluid dampers 61, 71, 91 becomes larger when moving, but conversely, the predetermined outer section is moved. The plurality of communication passages may be configured so that the damping force of the fluid damper is smaller when it is in the open state. Furthermore, the connection position of the plurality of communication paths to the cylinder is not limited to the example described so far, and an appropriate position is employed so that a desired damping force of the fluid damper can be obtained according to the movement position of the second piston. can do. Further, when a plurality of communication passages that bypass the second piston are provided in the fluid damper, a gear motor 52 and a rotary mass 53, a regulating valve 72, and a throttle may be provided in at least one of the plurality of communication passages. Of course. The variations related to the second communication path described so far also apply to the first communication path 10.

  In the first to fifth embodiments, the electric motors 13 and 33 are used as the drive sources for the first and second fluid pressure adjusting devices 12 and 32. However, hydraulic motors may be used. Further, in the first to fifth embodiments, gear pump type devices are used as the first and second fluid pressure adjusting devices 12 and 32, but other suitable fluid pressure adjusting devices such as vane pump type devices are used. Or a piston pump type described in FIG. 5 of Japanese Patent Application No. 2015-147612 by the present applicant, or described in paragraph [0049] of Japanese Patent No. 5191579, FIG. 2, or FIG. A screw pump type or the like may be used. In the first to fifth embodiments, the first and second fluid pressure adjusting devices 12 and 32 provided in the first and second communication passages 10 and 11 are used, but other appropriate devices, For example, the first to third fluid pressure pumps connected to the first to third fluid chambers and provided separately from each other may be used.

  Further, in the third, fourth and sixth embodiments, the gear motors 52 and 92 are used as the power conversion mechanism in the present invention. However, the flow of the working fluid HF is converted into rotational motion and transmitted to the rotational mass. Other suitable mechanisms, for example, a ball screw in which a piston described in FIG. 2 of Japanese Patent No. 5161395 by the present applicant is integrally provided on a nut, a vane motor, an impeller mechanism, or the like may be used.

  In the first to sixth embodiments, the first and second communication passages 10, 11, and 62 are connected to the peripheral wall 2a of the cylinder 2, but may be formed inside the peripheral wall. Furthermore, in the first to seventh embodiments (hereinafter collectively referred to as “embodiments”), the cross-sectional shape of the cylinder 2 and the first and second pistons 3 and 4 is circular, but may be square. Good. In the embodiment, the working fluid HF is silicon oil, but may be other appropriate fluids.

  Further, in the embodiment, the piston rod 5 is configured to extend outward from the second side wall 2c of the cylinder 2, but instead, it may be provided to extend outward from the first side wall. Or you may comprise so that it may extend outward from both the 1st and 2nd side walls. Moreover, in embodiment, although the piston rod 5 is used as a transmission member for transmitting external force to the 1st and 2nd pistons 3 and 4, a pair of other suitable members, such as steel wires, are used. A cable may be used. In that case, a cable guide hole penetrating in the axial direction is formed in the first and second side walls of the cylinder, and one of the pair of cables passes from the first piston through the cable guide hole in the first side wall. It is provided to extend outward, and the other of the pair of cables is provided to extend outward from the second piston through the cable guide hole in the second side wall. Furthermore, in this case, the first and second pistons may be connected using a rod or a cable. When connecting using a cable, the cable connecting the first and second pistons and both pistons are connected. The cable for transmitting the external force may be constituted by a single cable.

  Furthermore, in the embodiment, the fluid dampers 1, 31, 51, 61, 71, 91, 101 are provided so as to extend in the left-right direction on the upper and lower beams BU, BD via the V-shaped brace material BR. However, the upper and lower beams may be provided so as to extend in the left-right direction via an inverted V-shaped brace material. In either case, the pair of fluid dampers are opposed to each other from the brace material assembly. You may provide so that it may extend to the side. Alternatively, the fluid damper may be provided in a brace shape on the upper and lower beams, and may be provided so as to extend in the vertical direction in order to suppress vertical displacement between the upper and lower beams due to vibration. Alternatively, two fluid dampers may be provided on the upper and lower beams in a V shape or an inverted V shape.

  In the embodiment, the upper and lower beams BU and BD are respectively used as the objects to which the fluid dampers 1, 31, 51, 61, 71, 91, and 101 are connected, and the interlayer displacement between the two layers is suppressed. Other suitable sites may be employed. For example, the upper and lower beams provided with one or more beams between each other may be adopted as the objects to which the fluid damper is connected, and the interlayer displacement between three or more layers may be suppressed, or the building B You may employ | adopt each the foundation and beam which erected. Further, in the embodiment, by connecting the fluid dampers 1, 31, 51, 61, 71, 91, 101 to the beams BU, BD extending in the left-right direction, the displacement in the left-right direction due to the vibration of the building B is suppressed. However, you may suppress the displacement of the front-back direction by the vibration of a building by connecting with the beam extended in the front-back direction.

  Moreover, although embodiment is the example which applied the fluid damper 1, 31, 51, 61, 71, 91, 101 by this invention to the high-rise building B, this invention is not restricted to this, Other suitable structures It can also be applied to objects such as steel towers and bridges. Furthermore, in the embodiment, the fluid dampers 1, 31, 51, 61, 71, 91, and 101 are installed between the layers of the building B and used as vibration control devices. You may install between the support bodies to support and use as a seismic isolation apparatus.

  In the embodiment, the fluid dampers 1, 31, 51, 61, 71, 91, 101 have the first and second pistons 3, 4 and the first and second communication passages 10, 11 or the communication grooves 3 c and 4 c. However, three or more pairs of pistons and communication paths may be provided. In this case, it goes without saying that a fluid pressure adjusting device, a power conversion mechanism, a pressure regulating valve, and a throttle may be provided in these communication paths. Furthermore, it is needless to say that variations regarding the above embodiments may be applied in combination as appropriate. In addition, it is possible to appropriately change the detailed configuration within the scope of the gist of the present invention.

DESCRIPTION OF SYMBOLS 1 Fluid damper 2 Cylinder 2e 1st fluid chamber 2f 2nd fluid chamber 2g 3rd fluid chamber 3 1st piston 3c Communication groove (1st communication path)
4 2nd piston 4a 1st communicating hole (2nd communicating path, several communicating paths)
4b Second communication hole (second communication path, multiple communication paths)
4c Communication groove (second communication path)
8 1st pressure regulation valve 9 2nd pressure regulation valve 10 1st communicating path 11 2nd communicating path D1 1st predetermined section D2 2nd predetermined section HF Working fluid 31 Fluid damper 51 Fluid damper 52 Gear motor (power conversion mechanism)
53 Rotating mass 61 Fluid damper 62 Second communication path (multiple communication paths, bypass path)
D3 Third predetermined section (plural predetermined sections)
DO Predetermined outer section (multiple predetermined sections)
71 Fluid damper 91 Fluid damper 92 Gear motor (power conversion mechanism)
93 Rotating Mass 101 Fluid Damper

Claims (4)

A cylinder,
A first piston provided in the cylinder so as to be movable in the axial direction of the cylinder;
A first piston connected to the first piston with a gap in the axial direction, and a second piston provided in the cylinder so as to be movable in the axial direction;
In the cylinder, the first fluid chamber defined by the first piston, located on one side in the axial direction from the first piston, and the first and second pistons, There is provided at least a second fluid chamber between the first and second pistons and a third fluid chamber defined by the second piston and located on the other side in the axial direction with respect to the second piston. And
A working fluid filled in the first to third fluid chambers;
A first communication path that communicates with the first and second fluid chambers and allows a working fluid to flow between the first fluid chamber and the second fluid chamber;
A fluid damper, further comprising: a second communication path communicating with the second and third fluid chambers and allowing a working fluid to flow between the second fluid chamber and the third fluid chamber. The first piston is provided in the cylinder so as to be movable in the axial direction in a first predetermined section,
The second piston is provided in the cylinder so as to be movable in the axial direction in a second predetermined section aligned with the first predetermined section in the axial direction,
The second communication passage is configured by a plurality of communication passages, and the plurality of communication passages are configured such that when the second piston moves in a plurality of predetermined sections in the second predetermined section, the second fluid. The fluid damper according to claim 1, wherein the fluid damper is configured to flow a working fluid between a chamber and the third fluid chamber. The first communication path is configured to bypass the first piston and to communicate with the first fluid chamber and a portion of the second fluid chamber in the first predetermined section.
A rotatable mass,
A power conversion mechanism provided in the first communication path, which converts the flow of the working fluid in the first communication path into a rotational motion and transmits the rotational motion to the rotary mass, further comprising: The fluid damper as described. One of the plurality of communication passages bypasses the second piston when the second piston moves in a third predetermined section located inside the axial direction in the second predetermined section, The second fluid chamber is configured as a bypass passage that causes the working fluid to flow between a portion in the second predetermined section and the third fluid chamber,
The communication passages other than the bypass passage among the plurality of communication passages include a first communication hole and a second communication hole formed so as to penetrate the second piston in the axial direction.
The first communication hole is closed when the difference between the pressure of the working fluid in the second fluid chamber and the pressure of the working fluid in the third fluid chamber is smaller than a first predetermined value. A first pressure regulating valve that opens the first communication hole when the first predetermined value is reached,
The second communication hole closes the second communication hole when a difference between the pressure of the working fluid in the third fluid chamber and the pressure of the working fluid in the second fluid chamber is smaller than a second predetermined value. The fluid damper according to claim 2 or 3, further comprising a second pressure regulating valve that opens the second communication hole when the second predetermined value is reached.

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