JP4328317B2 - Damping hydraulic damper - Google Patents

Description

  The present invention relates to a damping hydraulic damper for a structure or the like that attenuates a vibration external force caused by an earthquake or a wind in accordance with discharge / suction of hydraulic oil in a pressure chamber of a cylinder.

  Conventionally, as disclosed in Patent Document 1, a vibration damping hydraulic damper includes a first pressure chamber and a second pressure chamber that are filled with hydraulic oil on both sides of a piston that reciprocates in a cylinder. A pressure regulating valve as a control valve is interposed in a flow path communicating with the chamber. When an external vibration force such as earthquake or wind acts, the piston reciprocates, the pressure in one of the pressure chambers rises, and hydraulic oil flows from this pressure chamber toward one of the other pressure chambers. As the oil flows, a damping force is generated by the pressure regulating valve, and a damping action against vibration is obtained to reduce the shaking of the building.

Then, an accumulator is accommodated in the piston rod provided on the piston, and the oil chamber of this accumulator is communicated with both pressure chambers via a pressure regulating valve and a check valve arranged in parallel with the pressure regulating valve, and both pressure chambers are filled. Absorb the thermal expansion of the hydraulic oil, or prevent the pressure chamber from becoming negative pressure by supplying hydraulic oil to one of the pressure chambers that increase in volume due to the reciprocating movement of the piston. ing.
JP 2004-36677 A (paragraph numbers 0012 to 0033 and FIG. 1)

  However, in such a conventional one, the accumulator is slidably inserted into the piston rod to form an oil chamber, and the free piston is urged toward the oil chamber to reduce the pressure in the oil chamber. It comprises a spring to be set and a gauge rod that protrudes from the back of the free piston so that the amount of oil in the oil chamber can be seen from the outside. On the outer periphery of the free piston, an annular seal member is provided in sliding contact with the inside of the piston rod so as to seal the oil chamber. When the free piston slides repeatedly during a long period of time when the hydraulic oil in the pressure chamber is absorbed into the oil chamber or the hydraulic oil is replenished from the oil chamber to the pressure chamber, the seal member wears and the hydraulic oil in the oil chamber is exposed to the outside. There was a risk that the pressure chamber would become negative due to insufficient hydraulic fluid to be supplied to the pressure chamber from the oil chamber.

  The subject of this invention is providing the hydraulic damper for damping | damping which can prevent the hydraulic fluid of the oil chamber of an accumulator from leaking outside by long-term use.

In order to achieve this problem, the present invention has taken the following measures in order to solve the problem. That is,
A cylinder provided with a first pressure chamber and a second pressure chamber formed on both sides of a reciprocating piston and filled with hydraulic oil; a control valve interposed in a flow path communicating the both pressure chambers; In a hydraulic damper for vibration suppression provided with an accumulator for supplying and discharging the hydraulic oil to and from a pressure chamber,
The accumulator includes the bellows formed in a metal cylindrical shape that can be expanded and contracted by elastic deformation, fixes one end of the bellows, closes the other end with a rigid lid member, and the lid member Can be moved according to the expansion and contraction of the bellows, an oil chamber is defined by the bellows and the lid member, the oil chamber is communicated with the pressure chambers, and the bellows is further deformed by the elastic deformation. This is a vibration damper for damping vibration characterized in that the hydraulic oil in the oil chamber can be pressurized .

The piston may be provided with a piston rod that penetrates the pressure chamber and protrudes to the outside, and the piston rod is provided with the accumulator. At this time, the accumulator may be attached to the tip of the piston rod protruding outside the pressure chamber, or the accumulator may be provided inside the piston rod .

The vibration damping hydraulic damper according to the present invention is formed by partitioning an oil chamber of an accumulator with a metal bellows that can be expanded and contracted by elastic deformation, and the bellows is used for supplying and discharging hydraulic oil between the pressure chamber and the oil chamber. Since it expands and contracts without coming into contact with the member, the bellows is not worn, and it is possible to satisfactorily prevent the hydraulic fluid in the oil chamber of the accumulator from leaking over a long period of use. In addition, since the bellows expands and contracts due to elastic deformation, it is possible to reduce the number of parts by eliminating the need for a spring that sets the pressure in the oil chamber by urging the free piston required by conventional vibration damping dampers. This makes it possible to reduce the cost in combination with the ease of manufacture. Furthermore, the bellows of the accumulator has a cylindrical shape, one end of the bellows is fixed, the other end is closed with a rigid lid member, and the lid member can be moved according to the expansion and contraction of the bellows. The pressure receiving surface can receive a high pressure, and a high pressure can be received well.

According to the second aspect of the present invention, since the accumulator is provided on the piston rod projecting to the outside, the whole can be made compact.
In the invention according to claim 3, since the accumulator is attached to the tip of the piston rod protruding outside, the expansion and contraction of the bellows accompanying the supply and discharge of the hydraulic oil between the pressure chamber and the oil chamber can be visually recognized from the outside. The amount of oil in the chamber can be confirmed, and a gauge rod for visually confirming the amount of oil in the oil chamber required by the conventional vibration damping damper can be eliminated, thereby simplifying the configuration.

In the invention according to claim 4, since the accumulator is provided inside the piston rod, the appearance can be improved without exposing the accumulator to the outside .

The best mode for carrying out the present invention will be described below in detail with reference to the drawings.
As shown in FIG. 1, reference numeral 1 denotes a cylinder. The cylinder 1 includes a cylinder body 4 in which a sliding hole 2 is formed, a pair of cover members 6 and 8 that close both ends of the sliding hole 2, and the sliding hole 2. And a piston 10 slidably inserted. A piston rod 12 penetrating both cover members 6 and 8 is integrally attached to the piston 10. The sliding hole 2 is partitioned by the piston 10 to form a first pressure chamber 14 and a second pressure chamber 16.

  The piston rod 12 includes a first rod portion 12a and a second rod portion 12b. The first rod portion 12a has one end inserted into the piston 10 and the other end covered from the first pressure chamber 14 side. The member 6 is slidably penetrated and protrudes to the outside of the cylinder body 4. A joint 22 is attached to the tip of the member 6.

  One end of the second rod portion 12b is inserted into the piston 10, and is screwed into one end of the first rod portion 10a, so that the first rod portion 12a, the second rod portion 12b, and the piston 10 are integrally fixed. ing. The other end of the second rod portion 12 b penetrates the cover member 8 from the second pressure chamber 16 side so as to be slidable and protrudes outside the cylinder body 4.

  A connecting member 24 is attached to the cover member 8 on the second rod portion 12 b side, and a bottomed hole 26 is formed in the connecting member 24. The bottomed hole 26 accommodates the second rod portion 12 b protruding from the cover member 8. A joint 28 is attached to the end of the connecting member 24 in the longitudinal direction. In the brace member installed in the construction surface of the structural body composed of the pillar and the beam, the joint 22 of the first rod portion 12a and the joint 28 of the connecting member 24 are on the axis, and one is on one end of the brace member. It is called a brace type that is attached and the other is attached to the structural body.

  As shown in FIG. 2, a first flow path 30 and a second flow path 32 that connect the first pressure chamber 14 and the second pressure chamber 16 are formed in the piston 10. A first check valve 34 is interposed in the first flow path 30 on the first pressure chamber 14 side, and a second check valve 36 is interposed on the second pressure chamber 16 side. The first check valve 34 allows the hydraulic oil to flow from the first pressure chamber 14 side to the second pressure chamber 16 side, and the second check valve 36 allows the second check valve 36 to flow from the second pressure chamber 16 side to the first pressure chamber 14 side. It is arranged to allow the flow of hydraulic oil.

  The second flow path 32 is provided with a third check valve 38 on the first pressure chamber 14 side and a fourth check valve 40 on the second pressure chamber 16 side. The third check valve 38 allows the hydraulic oil to flow from the second pressure chamber 16 side to the first pressure chamber 14 side, and the fourth check valve 40 allows the first pressure chamber 14 side to move to the second pressure chamber 16 side. It is arranged to allow the flow of hydraulic oil.

  The first flow path 30 between the first check valve 34 and the second check valve 36 and the second flow path 32 between the third check valve 38 and the fourth check valve 40 are the third flow. The third flow path 41 is provided with a pressure regulating valve 42 as a control valve. The pressure regulating valve 42 gives a predetermined fluid resistance to the hydraulic oil flowing from the first flow path 30 to the second flow path 32.

  Furthermore, a first relief valve 44 and a second relief valve 46 that connect the first pressure chamber 14 and the second pressure chamber 16 are provided in the piston 10, and the first relief valve 44 has a first pressure. The high pressure hydraulic oil is allowed to escape from the chamber 14 to the second pressure chamber 16, and the second relief valve 46 is arranged to allow the high pressure hydraulic oil to escape from the second pressure chamber 16 to the first pressure chamber 14.

  A connection flow path 48 is connected to the second flow path 32 between the third check valve 38 and the fourth check valve 40, and a throttle 50 is interposed in the connection flow path 48. The connection channel 48 is connected to a connection hole 52 formed in the first rod portion 12a, and the connection hole 52 communicates with a bottomed hole 54 formed at the end of the first rod portion 12a. The bottomed hole 54 communicates with a through hole 56 formed in the second rod portion 12b.

  The through hole 56 is formed so as to penetrate in the longitudinal direction of the second rod portion 12b, and an accumulator 58 connected to the through hole 56 is attached to the end of the second rod portion 12b. As shown in FIG. 3, the accumulator 58 includes a fixing member 60 screwed to the end of the second rod portion 12 b, and a supply / discharge hole 62 communicating with the through hole 56 is formed through the fixing member 60. .

  One end of a bellows 64 formed in a cylindrical shape is fixedly attached to the outer periphery of the fixing member 60, and the other end of the bellows 64 is fixedly attached to a lid member 66 having rigidity. Both ends of the bellows 64 are closed by the fixing member 60 and the lid member 66, and an oil chamber 68 communicating with the supply / discharge hole 62 is defined.

  The bellows 64 is formed by molding a metal material such as SUS304. The bellows 64 can be expanded and contracted by elastic deformation, and the volume of the oil chamber 68 is changed by expansion and contraction of the bellows 64, and the oil chamber 68 is expanded by elastic deformation. It is comprised so that hydraulic fluid can be pressurized. The lid member 66 is arranged to be movable according to the expansion and contraction of the bellows 64. As shown in FIG. 1, an observation window 70 is formed on the connection member 24 so that a lid member 66 that moves according to the expansion and contraction of the bellows 64 can be visually recognized from the outside.

Next, the operation of the above-described vibration damping hydraulic damper according to the first embodiment will be described.
First, when an external vibration force such as an earthquake or wind acts on the cylinder 1 and the piston 10 moves in a direction in which the volume of the first pressure chamber 14 decreases and the volume of the second pressure chamber 16 increases, for example, The pressure of the hydraulic oil in the chamber 14 increases. As a result, the hydraulic oil in the first pressure chamber 14 flows through the first flow path 30, the first check valve 34, the third flow path 41, the pressure regulating valve 42, the second flow path 32, and the fourth check valve 40. 2 flows into the pressure chamber 16. At that time, the second check valve 36 and the third check valve 38 regulate the flow of the hydraulic oil.

  When the hydraulic oil passes through the pressure regulating valve 42, the moving speed of the piston 10 is reduced by the flow path resistance. When the hydraulic oil pressure exceeds a predetermined pressure, the first relief valve 44 is also opened, and the hydraulic oil in the first pressure chamber 14 flows into the second pressure chamber 16 via the first relief valve 44. This prevents the hydraulic oil pressure from becoming high and damaging the equipment.

  When the direction of the external force changes, and conversely, the volume of the second pressure chamber 16 decreases and the piston 10 moves in a direction in which the volume of the first pressure chamber 14 increases, the hydraulic oil pressure in the second pressure chamber 16 increases. To do. As a result, the hydraulic oil in the second pressure chamber 16 passes through the first flow path 30, the second check valve 36, the third flow path 41, the pressure regulating valve 42, the second flow path 32, and the third check valve 38. 1 flows into the pressure chamber 14. At that time, the first check valve 34 and the fourth check valve 40 regulate the flow of hydraulic oil.

  When the hydraulic oil passes through the pressure regulating valve 42, the moving speed of the piston 10 is reduced by the flow path resistance. When the hydraulic oil pressure exceeds a predetermined pressure, the second relief valve 46 is also opened, and the hydraulic oil in the second pressure chamber 16 flows into the first pressure chamber 14 via the second relief valve 46. This prevents the hydraulic oil pressure from becoming high and damaging the equipment.

  When the piston 10 reciprocates due to the vibration external force, a damping force is generated according to the flow path resistance by the pressure regulating valve 42, and the vibration is attenuated. At this time, for example, when the hydraulic oil pressure in the second pressure chamber 16 becomes negative, the supply / exhaust hole 62, the through hole 56, the bottomed hole 54, the connection hole 52, the throttle 50, and the connection from the oil chamber 68 of the accumulator 58 are connected. The hydraulic oil is prevented from flowing into the second pressure chamber 16 via the flow path 48, the second flow path 32, and the third check valve 40, thereby reducing the damping action.

  Similarly, when the hydraulic oil pressure in the first pressure chamber 14 becomes negative, the hydraulic oil flows from the oil chamber 68 of the accumulator 58 into the first pressure chamber 14 to prevent the damping action from being lowered. . When the hydraulic oil flows out from the oil chamber 68, the bellows 64 reduces the volume of the oil chamber 68 by its own elastic force, and applies pressure to the hydraulic oil for discharge. Similarly, when the amount of hydraulic oil decreases due to the temperature change of the hydraulic oil, the hydraulic oil is supplied from the oil chamber 68 to the first pressure chamber 14 or the second pressure chamber 16.

  In addition, for example, when the amount of hydraulic oil increases due to thermal expansion due to temperature change of the hydraulic oil, the first flow path 30, the first check valve 34, and the third flow from the first pressure chamber 14 to the oil chamber 68 of the accumulator 58. The hydraulic oil flows through the flow path 41, the pressure regulating valve 42, the connection flow path 48, the throttle 50, the connection hole 52, the bottomed hole 54, the through hole 56, and the supply / discharge hole 62.

  Alternatively, from the second pressure chamber 16 to the oil chamber 68 of the accumulator 58, the first flow path 30, the second check valve 36, the third flow path 41, the pressure regulating valve 42, the connection flow path 48, the throttle 50, the connection hole 52, The hydraulic oil flows in through the bottomed hole 54, the through hole 56, and the supply / discharge hole 62. When the working oil flows into the oil chamber 68, the bellows 64 expands while being elastically deformed, the volume of the oil chamber 68 increases, and the flowing working oil is accommodated.

  As described above, the oil chamber 68 of the accumulator 58 is defined by the metal bellows 64 that can be expanded and contracted by elastic deformation, and the bellows 64 is supplied and discharged between the pressure chambers 14 and 16 and the oil chamber 68. In addition, since it expands and contracts without coming into contact with other members, the bellows 64 is not worn, and it is possible to satisfactorily prevent the hydraulic oil in the oil chamber 68 of the accumulator 58 from leaking over a long period of use.

  Further, since the bellows 64 expands and contracts due to elastic deformation, it is possible to reduce the number of parts by eliminating the need for a spring that sets the pressure of the oil chamber by urging the free piston required in the conventional vibration damping damper. Can be easily manufactured by molding and cost reduction can be achieved. Furthermore, since the accumulator 58 is provided on the second rod portion 12b of the piston rod 12 projecting to the outside, the whole can be made compact.

  By the expansion of the bellows 64 due to elastic deformation, the lid member 66 moves. By observing this movement from the observation window 70, it can be confirmed that the accumulator 58 is operating normally. Further, when the amount of hydraulic oil decreases due to leakage of hydraulic oil or the like, it is possible to know that the volume of the oil chamber 68 has decreased by observing the position of the lid member 66 from the observation window 70. By this, it is possible to know leaks. Therefore, it is possible to eliminate the need for a gauge rod for visually confirming the amount of oil in the oil chamber required by a conventional vibration damping hydraulic damper, and to simplify the configuration.

  Since the bellows 64 of the accumulator 58 has a cylindrical shape, one end of the bellows 64 is fixed and the other end is closed by a rigid lid member 66, and the lid member 66 can be moved according to the expansion and contraction of the bellows 64. The member 66 can be a pressure receiving surface that receives the pressure of the oil chamber 68, and high pressure can be received well.

  Next, a vibration damper for vibration damping according to a second embodiment different from the first embodiment described above will be described with reference to FIGS. The same members as those in the above-described embodiment are denoted by the same reference numerals, and detailed description thereof is omitted. The same applies hereinafter.

  In the second embodiment, the structure of the accumulator is different from that of the first embodiment described above, and each flow path 30, 32, 48 provided in the piston 10, each check valve 34, 36, 38, 40, pressure regulating valve 42, throttle The configuration of the relief valves 44 and 46 is the same as that of the first embodiment. In the second embodiment, a storage hole 72 is formed in the second rod portion 12 b so as to be connected to the through hole 56. A fixing member 74 is inserted into the storage hole 72 to close the storage hole 72, and a plug member 76 is screwed into the fixing member 74 to be fixed.

  One end of a bellows 78 housed in the housing hole 72 and formed in a cylindrical shape is fixed to the fixing member 74, and the other end of the bellows 78 is fixed to a rigid lid member 80. As described above, the bellows 78 is formed by molding a metal material such as SUS304, and the bellows 78 can be expanded and contracted by elastic deformation.

  The lid member 80 is configured to be movable in the accommodation hole 72, and is partitioned by the accommodation hole 72 of the second rod portion 12 b, the fixing member 74, the outside of the bellows 78, and the lid member 80, thereby forming an oil chamber 82. Has been. In the second embodiment, an accumulator 84 is configured by the storage hole 72, the fixing member 74, the bellows 78, and the lid member 80 of the second rod portion 12b.

  A gauge rod 86 is erected on the lid member 80, and the gauge rod 86 passes through the bellows 78 and slidably passes through the fixing member 74 and the plug member 76. By moving the gauge rod 86 together with the lid member 80 that moves according to the expansion and contraction of the bellows 78 and observing the position of the gauge rod 86 from the observation window 70, the amount of oil in the oil chamber 82 can be known.

  When hydraulic fluid is supplied from the oil chamber 82 of the accumulator 84 to the first pressure chamber 14 or the second pressure chamber 16, the bellows 78 is extended by its own elastic force, and the lid member 80 is moved to the through hole 56 side. The hydraulic oil is discharged from the oil chamber 82. Further, when hydraulic fluid flows from the first pressure chamber 14 or the second pressure chamber 16 into the oil chamber 82 of the accumulator 84, the hydraulic fluid flows into the storage hole 72 from the through hole 56, and the bellows 78 through the lid member 80. Is elastically deformed and reduced, and the volume of the oil chamber 82 is expanded to accommodate the hydraulic oil.

  Even in this case, the bellows 78 expands and contracts without contacting with other members when the hydraulic oil is supplied and discharged between the pressure chambers 14 and 16 and the oil chamber 82 as described above. Therefore, it is possible to satisfactorily prevent the hydraulic oil from leaking over a long period of use. Further, since the bellows 78 expands and contracts due to elastic deformation, the number of parts can be reduced without using a spring, and the bellows 78 can be easily manufactured by molding, thereby reducing the cost.

  Further, since the accumulator 84 is provided on the second rod portion 12b of the piston rod 12 projecting to the outside, the whole can be made compact, and the accumulator 84 is provided inside the second rod portion 12b of the piston rod 12. Therefore, the appearance can be improved without exposing the accumulator 84 to the outside.

  Since the bellows 78 of the accumulator 84 has a cylindrical shape, one end of the bellows 78 is fixed and the other end is closed with a rigid lid member 80, and the lid member 80 can be moved according to the expansion and contraction of the bellows 78. The member 80 can be a pressure receiving surface that receives the pressure of the oil chamber 82, and high pressure can be received well.

Next, a vibration damping hydraulic damper of a third embodiment different from the first and second embodiments described above will be described with reference to FIGS.
Also in the third embodiment, the configuration of the accumulator is different from the first and second embodiments described above, and each flow path 30, 32, 48 provided in the piston 10, each check valve 34, 36, 38, 40, pressure regulating valve. 42, the throttle 50, and the relief valves 44 and 46 are the same as those in the first and second embodiments. In the third embodiment, the second rod portion 12b is formed in a cylindrical shape, the outer periphery of the second rod portion 12b is inserted into the piston 10, and the first rod portion 12a is disposed on the inner periphery of the second rod portion 12b. Is screwed, and the first rod portion 12a and the second rod portion 12b are fixed integrally.

  The fixing member 88 inserted into the second rod portion 12 b is screwed into the bottomed hole 54 of the first rod portion 12 a, and the supply / discharge hole 90 formed through the fixing member 88 is formed in the bottomed hole 54. It is communicated.

  One end of a bellows 92 formed in a cylindrical shape is fixedly attached to the outer periphery of the fixing member 88, and the other end of the bellows 92 is fixedly attached to a lid member 94 having rigidity. Both ends of the bellows 92 are closed by the fixing member 88 and the lid member 94, and an oil chamber 96 communicating with the supply / discharge hole 90 is defined. In the third embodiment, an accumulator 98 is configured by the fixing member 88, the bellows 92, and the lid member 94.

  The bellows 92 is formed by molding a metal material such as SUS304, and the bellows 92 is configured to be stretchable by elastic deformation. The lid member 94 is disposed so as to be movable in the second rod portion 12b in accordance with the expansion and contraction of the bellows 92.

  A plug member 97 is screwed to the other end of the second rod portion 12b to close the inside of the second rod portion 12b, and a gauge rod 99 standing on the lid member 94 slides the plug member 97. It is movably penetrated. As shown in FIG. 6, an observation window 70 is formed in the connection member 24 so that the gauge rod 99 that moves according to the expansion and contraction of the bellows 92 can be visually recognized from the outside.

  Even in the case of the third embodiment, when the hydraulic oil is supplied from the oil chamber 96 of the accumulator 98 to the first pressure chamber 14 or the second pressure chamber 16, the bellows 92 is reduced by its own elastic force, and the lid member 94 is removed. The hydraulic oil is discharged from the oil chamber 96 by moving to the fixing member 88 side. Further, when hydraulic fluid flows from the first pressure chamber 14 or the second pressure chamber 16 into the oil chamber 96 of the accumulator 98, the hydraulic fluid flows from the supply / discharge hole 90, elastically deforms and expands the bellows 92, and the oil The volume of the chamber 96 is expanded to contain hydraulic oil.

  Even in this case, the bellows 92 expands and contracts without contact with other members when the hydraulic oil is supplied to and discharged from the pressure chambers 14 and 16 and the oil chamber 96 as described above. Therefore, it is possible to satisfactorily prevent the hydraulic oil from leaking over a long period of use. In addition, since the bellows 92 expands and contracts due to elastic deformation, the number of parts can be reduced without using a spring, and the bellows 92 can be easily manufactured by molding, thereby reducing the cost.

  Further, since the accumulator 98 is provided on the piston rod 12 projecting to the outside, the whole can be made compact, and the accumulator 98 is provided inside the second rod portion 12b of the piston rod 12, so that the accumulator 98 is provided. The appearance can be improved without being exposed to the outside.

  Since the bellows 92 of the accumulator 98 is cylindrical, one end of the bellows 92 is fixed and the other end is closed with a rigid lid member 94, and the lid member 94 can be moved according to the expansion and contraction of the bellows 92. The member 94 can be a pressure receiving surface that receives the pressure of the oil chamber 96, and high pressure can be received well.

Next, a vibration damper for vibration damping according to a fourth embodiment different from the first to third embodiments described above will be described with reference to FIGS.
As shown in FIG. 8, reference numeral 100 denotes a cylinder. The cylinder 100 includes a cylinder main body 104 in which a sliding hole 102 is formed, a pair of cover members 106 and 108 that block both ends of the sliding hole 102, and the sliding hole 102. And a piston 110 slidably inserted. The piston 110 is integrally provided with a piston rod 112 that penetrates both the cover members 106 and 108. In the fourth embodiment, the piston 110 and the first rod portion 112a are integrally formed, and the second rod portion 112b is screwed into the piston 110 to be integrally formed.

  A joint member 116 is screwed to one end of the first rod portion 112 a of the piston rod 112. A connecting member 117 is attached to one end of the cylinder body 104 opposite to the joint member 116, and a joint member 118 is screwed to the end of the connecting member 117. One of the joint members 116, 118 is attached to an auxiliary member such as a mounting brace, and the other is called a shear link type attached to the structural body. What is the brace type shown in the first to third embodiments described above? Is different.

  The sliding hole 102 is partitioned by the piston 110 to form a first pressure chamber 124 and a second pressure chamber 126, and the cylinder body 104 communicates with the first pressure chamber 124 and the second pressure chamber 126. A first supply / discharge port 128 and a second supply / discharge port 130 are formed. The first supply / discharge port 128 and the second supply / discharge port 130 are formed in an opening on a mounting surface 132 formed flat on the outer periphery of the cylinder body 104.

  A first connection hole 144 and a second connection hole 146 are formed in the lower surface 138 a of the valve block 138 attached to the attachment surface 132 so as to communicate with the first supply / discharge port 128 and the second supply / discharge port 130. Yes. Connected to the first connection hole 144 and the second connection hole 146 are a first communication hole 148 and a second communication hole 150 which are formed in the valve block 138 in parallel at predetermined intervals. A first flow path 156 and a second flow path 158 are formed by the first connection hole 144, the second connection hole 146, the first communication hole 148, and the second communication hole 150.

  In the valve block 138, as shown in FIG. 11, a pair of first pressure regulating valve 160 and second pressure regulating valve 162 that are opposite to each other are provided between the first communication hole 148 and the second communication hole 150. Is formed. Further, in the valve block 138, a third pressure regulating valve 174 and a fourth pressure regulating valve 176 (see FIG. 12) having the same configuration as the first pressure regulating valve 160 and the second pressure regulating valve 162 are formed at symmetrical positions. .

  Although the first pressure regulating valve 160 and the second pressure regulating valve 162 are different in that they are provided in opposite directions, the configurations thereof are the same, and the third pressure regulating valve 174 and the fourth pressure regulating valve 176 are the same. The first pressure regulating valve 160 will be described in detail, and the second to fourth pressure regulating valves 162, 174, and 176 will be denoted by the same reference numerals and detailed description thereof will be omitted.

  The first pressure regulating valve 160 includes a valve body 166 in which a needle-like portion 166 a is inserted from the first communication hole 148 side into a through hole 164 that communicates with the first communication hole 148 and the second communication hole 150. The valve body 166 is urged in the direction in which the needle-like portion 166a is inserted into the through hole 164 by the compression spring 170 housed in the screwed support member 168. Further, the adjustment member 172 screwed to the support member 168 is rotated so that the urging force of the compression spring 170 can be adjusted.

  The needle-like portion 166a includes a straight portion and a groove deeper toward the tip. When the needle-like portion 166a is inserted into the through-hole 164, the through-hole 164 is closed by the straight portion, and the needle-like portion 166a is The groove is formed so that the opening area of the through-hole 164 is increased by the groove as it comes out of the through-hole 164.

  On the other hand, in the valve block 138, as shown in FIG. 10, a pair of first relief valve 178 and second relief valve 180 opposite to each other are provided between the first communication hole 148 and the second communication hole 150. Is formed. Further, a third relief valve 179 and a fourth relief valve 181 (see FIG. 12) having the same structure as the first relief valve 178 and the second relief valve 180 are formed in the valve block 138 at symmetrical positions.

  Although the first relief valve 178 and the second relief valve 180 are different in that they are provided in opposite directions, the configuration is the same, and the third relief valve 179 and the fourth relief valve 181 are also the same. The first relief valve 178 will be described in detail, and the second to fourth relief valves 179 to 181 will be denoted by the same reference numerals and detailed description thereof will be omitted.

  The first relief valve 178 includes a valve seat member 184 inserted from the first communication hole 148 side into a through hole 182 communicating with the first communication hole 148 and the second communication hole 150, and in the axial direction of the valve seat member 184. Has a discharge hole 186 formed therethrough. A valve body 188 is slidably inserted into a cylindrical member 190 inserted in the valve block 138 against the valve seat member 184 protruding into the first communication hole 148.

  The distal end of the tubular member 190 is in contact with the valve seat member 184, and a valve chamber 192 surrounded by the valve seat member 184, the tubular member 190, and the valve body 188 is formed. The valve chamber 192 is communicated with the first communication hole 148 via a discharge hole 194 formed in the cylindrical member 190 at the tip of the valve seat member 184 side.

  A support member 196 is screwed into the valve block 138, and a compression spring 200 is accommodated in a bottomed hole 198 formed in the support member 196. By this compression spring 200, the valve body 188 is urged so as to be seated on the valve seat 184a. The adjustment member 201 screwed to the support member 196 is rotated so that the biasing force of the compression spring 200 can be adjusted. The bottomed hole 198 is connected to the first communication hole 148 through the small diameter hole 202 and the through hole 182 of the second relief valve 180.

  On the other hand, the accumulator block 140 stacked on the valve block 138 is provided with an accumulator 203. The accumulator 203 includes a fixing member 204 attached to the accumulator block 140, and the fixing member 204 is formed in a cylindrical shape. One end of the bellows 206 is fixed. The other end of the bellows 206 is fixed to a rigid lid member 208, and an oil chamber 210 is defined by the fixing member 204, the bellows 206, and the lid member 208. The bellows 206 is formed by molding a metal material such as SUS304, and the bellows 206 is configured to be stretchable by elastic deformation.

  The oil chamber 210 is communicated with a connection hole 214 formed in the accumulator block 140 via a supply / discharge hole 212 formed in the fixing member 204. A pair of guide rods 216 and 218 are erected on the fixed member 204, and the lid member 208 is slidably supported by the pair of guide rods 216 and 218.

  Both ends of the stopper member 219 are fixed to the distal ends of the pair of guide rods 216 and 218, and the stopper member 219 is stretched between the pair of guide rods 216 and 218. When the bellows 206 is extended and the lid member 208 is moved, the lid member 208 abuts against the stopper member 219 to restrict further extension of the bellows 206.

  As shown in FIG. 12, the accumulator block 140 is provided with a first check valve 220 and a second check valve 222, and a first throttle 224 and a second throttle 226. The first pressure chamber 124 and the oil chamber 210 of the accumulator 203 are connected via a first check valve 220 and a first throttle 224, and the first check valve 220 is hydraulic fluid from the oil chamber 210 to the first pressure chamber 124. It is arranged to allow the flow of. Further, the second pressure chamber 126 and the oil chamber 210 of the accumulator 203 are connected via a second check valve 222 and a second throttle 226, and the second check valve 222 is connected from the oil chamber 210 to the second pressure chamber 126. It is arranged to allow the flow of hydraulic oil.

Next, the operation of the hydraulic damper according to the fourth embodiment will be described.
First, when an external vibration force such as an earthquake or wind acts on the cylinder 100 and, for example, the pressure in the second pressure chamber 126 rises, the cylinder 100 passes through the second supply / discharge port 130, the second connection hole 146, and the second communication hole 150. The acting force against the compression spring 170 acts on the valve body 166 of the first pressure regulating valve 160.

  When the acting force due to the pressure rise exceeds the urging force of the compression spring 170, the needle-like portion 166 a of the valve body 166 slides in the direction of coming out of the through hole 164. Thus, the second communication hole 150 communicates with the first communication hole 148 via the through hole 164 and further communicates with the first pressure chamber 124 via the first connection hole 144 and the first supply / discharge port 128.

  The pressure introduced from the second pressure chamber 126 and the urging force of the compression spring 170 act on the valve body 166 so that the valve body 166 slides when the acting force by the pressure exceeds the urging force. Since the urging force of the compression spring 170 is increased by sliding, the sliding amount of the valve body 166 is determined by the balance between the acting force due to the pressure and the urging force of the compression spring 170.

  Accordingly, the opening area of the through hole 164 by the needle-like portion 166a is also determined, so that the opening area gradually increases as the hydraulic oil pressure increases. As a result, in addition to the action of the second throttle 226, a linear relationship between the flow rate and the pressure is obtained in which the pressure increases almost in proportion to the discharge flow rate from the second pressure chamber 126, and the resistance corresponding to the vibration speed is reduced. As a result, an effective damping action against vibration can be exhibited.

  The pressure in the second pressure chamber 126 acts on the valve body 188 of the first relief valve 178 via the second supply / discharge port 130, the second connection hole 146, the second communication hole 150, the through hole 182, and the discharge hole 186. . When the pressure further increases and exceeds the urging force of the compression spring 200, the valve body 188 slides against the urging force of the compression spring 200. Therefore, the valve body 188 is separated from the valve seat 184a, and the discharge hole 186 and the first communication hole 148 are communicated with each other via the valve chamber 192 and the discharge hole 194.

  Accordingly, the hydraulic oil in the second pressure chamber 126 flows through the second supply / discharge port 130, the second connection hole 146, the second communication hole 150, the through hole 182, the discharge hole 186, the valve chamber 192, the discharge hole 194, and the first communication hole. It flows into the first pressure chamber 124 through the hole 148, the first connection hole 144, and the first supply / discharge port 128. Thus, when the pressure in the second pressure chamber 126 exceeds the relief pressure of the first relief valve 178, the first relief valve 178 is opened so that the pressure in the second pressure chamber 126 does not increase any more. To do. As a result, when the pressure exceeds the relief pressure, the resistance to vibration is kept constant. The same applies when the pressure in the first pressure chamber 124 increases due to vibration.

  When the pressure in the first pressure chamber 124 decreases due to vibration, the accumulator 203 operates from the oil chamber 210 to the first pressure chamber 124 via the supply / discharge hole 212, the first check valve 220, and the first supply / discharge port 128. Oil is supplied. This prevents the first pressure chamber 124 from becoming negative pressure and reducing the damping action. Similarly, when the pressure in the second pressure chamber 126 decreases, hydraulic oil is supplied to the second pressure chamber 126 via the supply / discharge hole 212, the second check valve 222, and the second supply / discharge port 130.

  On the other hand, when the temperature of the hydraulic fluid rises due to a rise in the temperature of the surrounding environment such as a rise in temperature, and the pressure in the first pressure chamber 124 and the second pressure chamber 126 rises, the first supply / discharge port 128 and the second supply port 128 The hydraulic oil is discharged into the oil chamber 210 through the exhaust port 130, the first connection hole 144 and the second connection hole 146, the first communication hole 148 and the second communication hole 150, the first throttle 224 and the second throttle 226. .

  Therefore, the bellows 206 is extended by elastic deformation, and the volume of the oil chamber 210 is increased to accommodate the hydraulic oil from the first pressure chamber 124 and the second pressure chamber 126. Conversely, when the temperature of the hydraulic oil decreases due to a decrease in the ambient temperature and the pressure in the first pressure chamber 124 and the second pressure chamber 126 decreases, the oil chamber 210 changes the first pressure chamber 124 and the second pressure chamber 126. Hydraulic oil is supplied. The remaining amount of hydraulic oil in the oil chamber 210 can be known from the amount of movement of the lid member 208.

  Even in this case, since the bellows 206 expands and contracts without contacting with other members when the hydraulic oil is supplied to and discharged from the pressure chambers 124 and 126 and the oil chamber 210 as described above, the bellows 206 is worn. Therefore, it is possible to satisfactorily prevent the hydraulic oil from leaking over a long period of use. In addition, since the bellows 206 expands and contracts due to elastic deformation, the number of parts can be reduced without the need for a spring, and the bellows 206 can be easily manufactured by molding, thereby reducing the cost.

  Since the bellows 206 of the accumulator 203 has a cylindrical shape, one end of the bellows 206 is fixed and the other end is closed with a rigid lid member 208, and the lid member 208 is movable according to the expansion and contraction of the bellows 206. The member 208 can be a pressure receiving surface that receives the pressure of the oil chamber 210, and a high pressure can be received well.

  As described above, the present invention is not limited to such an embodiment, and can be implemented in various modes without departing from the gist of the present invention. In the first to fourth embodiments described above, the control valve is used as a control valve. Although the pressure regulating valves 42, 160, 162, 174, and 176 are used, it is needless to say that an on-off valve disclosed in Japanese Patent No. 3357624 may be used as a control valve.

It is sectional drawing of the hydraulic damper for damping | damping as 1st Embodiment of this invention. It is an expanded sectional view of the piston of the hydraulic damper for damping as a 1st embodiment. It is an expanded sectional view of the accumulator of the hydraulic damper for damping as a 1st embodiment. It is sectional drawing of the hydraulic damper for damping | damping as 2nd Embodiment of this invention. It is an expanded sectional view of the accumulator of the hydraulic damper for damping as a 2nd embodiment. It is sectional drawing of the hydraulic damper for damping | damping as 3rd Embodiment of this invention. It is an expanded sectional view of the accumulator of the hydraulic damper for damping as a 3rd embodiment. It is sectional drawing of the hydraulic damper for damping | damping as 4th Embodiment of this invention. It is a top view which shows a part of damping hydraulic damper as 4th Embodiment in a cross section. It is an expanded sectional view of the relief valve and accumulator of the damping hydraulic damper as a 4th embodiment. It is an expanded sectional view of the pressure regulation valve of the hydraulic damper for damping as a 4th embodiment. FIG. 9 is a hydraulic circuit diagram of a vibration damping hydraulic damper as a fourth embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,100 ... Cylinder 2,102 ... Sliding hole 4,104 ... Cylinder main body 6,8,106,108 ... Cover member 10,110 ... Piston 12,112 ... Piston rod 14,124 ... First pressure chamber 16,126 ... second pressure chambers 34, 36, 38, 40, 220, 222 ... check valves 42, 160, 162, 174, 176 ... pressure regulating valves 44, 46, 178-181 ... relief valves 50, 224, 226 ... throttle 58, 84, 98, 203 ... accumulators 60, 74, 88, 204 ... fixing members 62, 90, 212 ... supply / discharge holes 64, 78, 92, 206 ... bellows 66, 80, 94, 208 ... lid members 68, 82, 96 , 210 ... Oil chamber 70 ... Observation window 72 ... Storage hole 86, 99 ... Gauge rod 138 ... Valve block 140 ... Accumulator block 216, 218 ... Guide rod 19 ... stopper member

Claims (4)

A cylinder provided with a first pressure chamber and a second pressure chamber formed on both sides of a reciprocating piston and filled with hydraulic oil; a control valve interposed in a flow path communicating the both pressure chambers; In a hydraulic damper for vibration suppression provided with an accumulator for supplying and discharging the hydraulic oil to and from a pressure chamber,
The accumulator includes the bellows formed in a metal cylindrical shape that can be expanded and contracted by elastic deformation, fixes one end of the bellows, closes the other end with a rigid lid member, and the lid member Can be moved according to the expansion and contraction of the bellows, an oil chamber is defined by the bellows and the lid member, the oil chamber is communicated with the pressure chambers, and the bellows is further deformed by the elastic deformation. A hydraulic damper for vibration control characterized in that the hydraulic oil in the oil chamber can be pressurized .   The vibration damper according to claim 1, wherein the piston is provided with a piston rod that passes through the pressure chamber and protrudes to the outside, and the accumulator is provided on the piston rod.   3. The vibration damper for damping vibration according to claim 2, wherein the accumulator is attached to a tip end of the piston rod protruding outside the pressure chamber.   The damping hydraulic damper according to claim 2, wherein the accumulator is provided inside the piston rod.

Images