JP5464758B2 - Hydraulic damper - Google Patents

Description

  The present invention relates to a hydraulic damper that is attached to a structure such as a building and used to absorb displacement between positions of the structure due to an external force such as an earthquake.

  In the conventional hydraulic damper, for example, as shown in FIG. 11, there is a hydraulic damper 2 for damping that is used to absorb the displacement between positions of the structure due to an external force such as an earthquake to suppress the vibration. .

  The conventional hydraulic damper 2 includes a cylindrical cylinder 4 closed at both ends, and a space formed inside the cylinder 4 and formed in the cylinder 4 into two spaces. Piston 6 which forms the two oil chambers 8 and 10 with which hydraulic oil was filled in the space in the both sides was provided.

  This piston 6 has two piston rods 12 and 14 extending from the both end faces 6a and 6b to the outside in the axial direction (left and right direction in FIG. 11), and these piston rods 12 and 14 are cylinders. Each end portion protruded outward in the axial direction from both end faces 4a and 4b. And the front-end | tip part of the piston rod 14 was accommodated in the internal space of the extension member 16 extended from the end surface 4b of the cylinder 4 to the outer side of an axial direction.

  The conventional hydraulic damper 2 is a relief that controls the flow state of the hydraulic fluid between the oil chambers 8 and 10 in the middle of the oil passage inside the piston 6 that communicates between the oil chambers 8 and 10. Valves 18 and 20 were provided. The internal space of the piston rod 14 of the piston 6 was provided with an accumulator 22 that absorbs expansion and contraction of the hydraulic oil in the oil chambers 8 and 10 to operate the hydraulic damper 2 stably.

  The accumulator 22 includes an accumulator piston 26 that divides the internal space of the piston rod 14 into two spaces, and an accumulator oil that is formed in one of the two spaces and communicates with the two oil chambers 8 and 10 through an oil passage. A chamber 28 and a spring 28 that is housed in the other of the two spaces and presses the accumulator piston 26 toward the accumulator oil chamber 24; and is integrally connected to the accumulator piston 26 in the axial direction thereof, and its tip is It was comprised with the rod-shaped member 30 protruded outside from the axial hole of piston rod 14 front-end | tip part.

  The amount of hydraulic oil in the oil chambers 8 and 10 in the cylinder 4 is determined by the amount of the rod-shaped member 30 protruding from the front end surface of the piston rod 14 through the hydraulic oil in the accumulator oil chamber 24 of the accumulator 22. It has become possible to monitor by a change in the length dimension (see Patent Document 1).

  In order to make it possible to visually recognize a change in the length of the protrusion of the rod-shaped member 30 protruding from the shaft hole at the tip of the piston rod 14 from the tip of the piston rod 14, the extension member 16 includes an inner portion thereof. The through-hole 16a for looking into the protrusion length of the rod-shaped member 30 was formed.

  Since such a conventional hydraulic damper 2 has the relief valves 18 and 20 and the accumulator 22 provided therein, it is not necessary to provide those parts outside the outer peripheral surface in the radial direction of the cylinder 4. These parts can be prevented from interfering with other members around the hydraulic damper 2.

JP 2004-036667 A

  However, in the conventional hydraulic damper 2, as described above, since the rod-shaped member 30 is integrally provided on the accumulator piston 26 of the accumulator 22, in order to ensure the operating range of the rod-shaped member 30, the cylinder Since the length of the four extending members 16 in the axial direction needs to be increased accordingly, the hydraulic damper 2 is large, heavy, and expensive.

  In order to solve the problems of the conventional hydraulic damper 2 described above, another conventional pressure gauge 42 is provided on the outer peripheral portion of the cylinder 4 as shown in FIG. The hydraulic damper 40 was devised.

  The pressure detector 42 of the pressure gauge 42 communicates with the oil chamber 8 in the cylinder 4 through a flow path 44 formed in the cylindrical outer periphery of the cylinder 4 so as to open in the radial direction. The pressure of the hydraulic oil in the oil chamber 8 can be directly detected.

  In such a conventional hydraulic damper 40, the amount of hydraulic oil in the oil chambers 8, 10 in the cylinder 4 and the accumulator oil chamber 24 is controlled by detecting a change in the pressure in the oil chamber 8 in the cylinder 4. Therefore, it is possible to prevent the hydraulic damper 40 from being large, heavy and expensive.

  However, in the conventional hydraulic damper 40, as shown in FIG. 12, the pressure gauge 42 is provided so as to protrude radially outward from the outer peripheral portion of the cylinder 4, so in the longitudinal direction of the hydraulic damper 40. There is a problem that the vertical radial dimension becomes large and the pressure gauge 42 may interfere with other members around the cylinder 4.

  Further, in the conventional hydraulic damper 40, since the pressure gauge 42 is provided so as to protrude radially outward from the outer peripheral portion of the cylinder 4, there is a problem that the appearance of the hydraulic damper 40 is significantly impaired.

  Further, during normal operation, the hydraulic damper 40 is not operated, that is, since the piston 6 does not move in the cylinder 4, the pressure of the hydraulic oil in the oil chamber 8 of the cylinder 4 is low. Since the pressure fluctuation due to the hydraulic oil leakage is minute, it is necessary to make the pressure gauge 42 have high measurement accuracy in the low pressure range in order to detect the hydraulic oil leakage.

  However, when an external force such as an earthquake is applied to the structure provided with the hydraulic damper 40 and the piston 6 moves in the cylinder 4, the oil chamber 8 of the cylinder 4 is applied with a large force by the piston 6. Since the pressure of the internal hydraulic fluid rises at a stretch, if the pressure gauge 42 with high measurement accuracy is used in the low pressure range as described above, a pressure higher than the allowable high pressure side pressure is received. There is a problem that the pressure gauge 42 may be damaged or its measurement accuracy and life may be reduced.

  In addition, when the pressure gauge 42 capable of measuring a wide range of pressure from the low pressure to the high pressure of the hydraulic oil in the oil chamber 8 that is not damaged when the hydraulic damper 40 is operated, the measurement accuracy is low in the low pressure range. There has been a problem that minute pressure fluctuations due to hydraulic oil leakage when the damper 40 is not operated cannot be detected.

  In view of the above problems, the present invention can easily recognize the change in the amount of hydraulic oil in the hydraulic damper from the outside, and the hydraulic damper is large, heavy, expensive, It is possible to prevent the parts from interfering with other members around the hydraulic damper and the appearance of the hydraulic damper to be remarkably impaired, and to prevent the oil amount monitoring means from being damaged and the life of the hydraulic damper from being reduced during the operation of the hydraulic damper. It is an object of the present invention to provide a hydraulic damper that can improve the measurement accuracy of the oil amount monitoring means when the hydraulic damper is not in operation.

In order to solve the above-described problem, a hydraulic damper according to the present invention includes:
A cylinder formed in a cylindrical shape closed at both ends;
A piston having a first piston rod portion, and a second piston rod portion projecting from each of both axial ends of the cylinder housed in the cylinder on the outside of the cylinder,
Two oil chambers formed on both sides in the axial direction of the piston in the cylinder and filled with hydraulic oil inside;
An accumulator having an accumulator oil chamber provided in the second piston rod portion and communicating with two oil chambers in the cylinder through a flow path;
In the outer peripheral portion of the first piston rod part, axially outward from an end portion of said cylinder, and detachably provided radially inward of the cylinder, without passing through the accumulator oil chamber, wherein in said cylinder 2 Oil amount monitoring means communicating with one of the oil chambers on the first piston rod portion side through a flow path formed in the first piston rod portion ;
An opening that allows the oil amount monitoring means to be attached and detached from the outside is formed, and includes a covering member that is provided so as to cover an outer peripheral surface of the cylinder and the first piston rod portion. is there.

The hydraulic damper according to the present invention is
A cylinder formed in a cylindrical shape closed at both ends;
A piston having a first piston rod portion and a second piston rod portion that are housed in the cylinder and project from the both ends in the axial direction of the cylinder to the outside of the cylinder;
Two oil chambers formed on both sides in the axial direction of the piston in the cylinder and filled with hydraulic oil inside;
An accumulator having an accumulator oil chamber provided in the second piston rod portion and communicating with two oil chambers in the cylinder through a flow path;
One end is connected to the tip of the first piston rod part, and the mounting part has an axial hole penetrating in the axial direction of the first piston rod part,
A fixed plate portion that is connected to the other end portion of the attachment portion, opens to the attachment portion side, and has an opening that penetrates in the plate thickness direction;
The shaft hole of the mounting portion and the opening of the fixing plate portion are disposed in a gap formed on the outer side in the axial direction than the end portion of the cylinder and on the inner side in the radial direction of the cylinder. Detachably provided at the tip of the first piston rod part inserted halfway in the axial direction of the shaft hole of the part, and the second of the two oil chambers in the cylinder without the interposition of the accumulator oil chamber. An oil amount monitoring means that communicates with one side of the first piston rod portion through a flow path formed in the first piston rod portion;
And a covering member provided so as to cover an outer peripheral surface of the cylinder and the first piston rod portion .

The hydraulic damper according to the present invention is
A cylinder formed in a cylindrical shape closed at both ends;
A piston having a first piston rod portion and a second piston rod portion that are housed in the cylinder and project from the both ends in the axial direction of the cylinder to the outside of the cylinder;
Two oil chambers formed on both sides in the axial direction of the piston in the cylinder and filled with hydraulic oil inside;
An accumulator having an accumulator oil chamber provided in the second piston rod portion and communicating with two oil chambers in the cylinder through a flow path;
A connecting member having one end connected to the tip of the first piston rod portion and the other end connected to a ball joint;
It is disposed on the outer side in the axial direction from the end of the cylinder and on the inner side in the radial direction of the cylinder, and is detachably provided on the outer peripheral part of the connecting member, and without the accumulator oil chamber, Oil amount monitoring means communicating with one of the two oil chambers on the first piston rod portion side through flow paths respectively formed in the first piston rod portion and the connecting member;
And a covering member provided so as to cover an outer peripheral surface of the cylinder and the first piston rod portion .

The hydraulic damper according to the present invention is
A cylinder formed in a cylindrical shape closed at both ends;
A piston having a first piston rod portion and a second piston rod portion that are housed in the cylinder and project from the both ends in the axial direction of the cylinder to the outside of the cylinder;
Two oil chambers formed on both sides in the axial direction of the piston in the cylinder and filled with hydraulic oil inside;
An accumulator having an accumulator oil chamber provided in the second piston rod portion and communicating with two oil chambers in the cylinder through a flow path;
A fitting hole penetrating in the axial direction of the first piston rod portion through which the first piston rod portion is inserted, and closing an end portion of the cylinder on the first piston rod portion side; and the first piston rod A cover member formed with a flow path penetrating in the axial direction of the portion;
The two oils in the cylinders are disposed on the outer side in the axial direction from the ends of the cylinders and on the inner side in the radial direction of the cylinders, and are detachably attached to the cover member without interposing the accumulator oil chamber. An oil amount monitoring means communicating with one of the first piston rod part side of the chamber through the flow path of the cover member;
An opening that allows the oil amount monitoring means to be attached and detached from the outside is formed, and includes a covering member that is provided so as to cover an outer peripheral surface of the cylinder and the first piston rod portion. is there.

Moreover, the hydraulic damper according to the present invention is characterized in that the oil amount monitoring means is detachably provided through connection / separation of a pair of joint members .

  The hydraulic damper according to the present invention is characterized in that the oil amount monitoring means includes a pressure gauge for detecting the pressure of the hydraulic oil in the oil chamber.

  Further, the hydraulic damper according to the present invention is characterized in that the oil amount monitoring means includes a bellows cylindrical member that expands and contracts in its own axial direction in accordance with the pressure of the hydraulic oil in the oil chamber.

The hydraulic damper according to the present invention is
The oil amount monitoring means is
A housing having a space inside,
A third oil chamber that is housed in the space and that divides the space into two spaces and communicates with one of the two oil chambers on the first piston rod side is formed in one of the two spaces. A third piston;
An elastic member housed in the other of the two spaces so as to press the third piston toward the third oil chamber;
A rod-shaped member provided integrally with the third piston and capable of projecting to the outside of the housing;
The amount of protrusion of the rod-shaped member to the outside of the casing varies according to the variation of the pressure of the hydraulic oil in one of the two oil chambers.

According to such a hydraulic damper of the present invention,
A cylinder formed in a cylindrical shape closed at both ends;
A piston having a pair of piston rods housed in the cylinder and projecting from the both ends in the axial direction of the cylinder to the outside of the cylinder;
Two oil chambers formed on both sides in the axial direction of the piston in the cylinder and filled with hydraulic oil inside;
One of the pair of piston rods is provided detachably on the outer side in the axial direction than one end of the cylinder and on the inner side in the radial direction of the cylinder, and communicates with one of the two oil chambers. By having
In addition to being able to easily recognize the change in the amount of hydraulic oil in the hydraulic damper from the outside, the hydraulic damper is large, heavy and expensive, and its own parts interfere with other members around the hydraulic damper In addition, the appearance of the hydraulic damper can be prevented from being remarkably impaired, the oil amount monitoring means can be prevented from being damaged or the life of the hydraulic damper can be reduced during the operation of the hydraulic damper, and the hydraulic damper can be prevented from being operated. The measurement accuracy of the oil amount monitoring means can be improved.

It is sectional drawing which shows the hydraulic damper 50 which concerns on the 1st Embodiment of this invention along the axis line. It is a partial expanded sectional view which expands and shows the front-end | tip part of the 1st piston rod part 62 of the piston 60 shown in FIG. It is a partial expanded sectional view which expands and shows the pressure gauge 90 attachment part of the 1st piston rod part 62 shown in FIG. FIG. 2 is a partially enlarged cross-sectional view showing a pressure gauge 90 mounting portion of the first piston rod portion 62 shown in FIG. 1 in an enlarged manner, and showing a state in which the second joint 110 is detached from the first joint 102 and disassembled. It is a partial expanded sectional view which expands and shows the front-end | tip part of the 1st piston rod part 124 of piston 122 in the hydraulic damper 120 which concerns on the 2nd Embodiment of this invention. It is sectional drawing which shows the hydraulic damper 140 which concerns on the 3rd Embodiment of this invention along the axis line. It is a partial expanded sectional view which expands and shows the front-end | tip part of the 1st piston rod part 144 of the piston 142 shown in FIG. It is a partial expanded sectional view which expands and shows the front-end | tip part of the 1st piston rod part 164 of the piston 162 in the hydraulic damper 160 which concerns on the 4th Embodiment of this invention. It is a partial expanded sectional view which expands and shows the oil quantity monitoring means 182 attached to the 2nd coupling 110 in the hydraulic damper 180 which concerns on the 5th Embodiment of this invention. It is a partial expanded sectional view which expands and shows the oil quantity monitoring means 202 attached to the 2nd coupling 110 in the hydraulic damper 200 which concerns on the 5th Embodiment of this invention. It is sectional drawing which shows the conventional hydraulic damper 2 along the axis line. It is sectional drawing which shows the other conventional hydraulic damper 40 along the axis line.

  Hereinafter, the form for implementing the hydraulic damper concerning the present invention is explained concretely based on a drawing.

  FIG. 1 to FIG. 4 are diagrams that are referred to for explaining a hydraulic damper 50 for vibration control according to the first embodiment of the present invention.

  As shown in FIG. 1, the hydraulic damper 50 according to the first embodiment of the present invention includes a cylindrical cylinder body 54 and a pair of cover members 56 and 58 that close both ends of the cylinder body 54 in the axial direction. And a piston 60 is housed inside the cylinder 52.

  The piston 60 is formed in a short cylindrical shape having an axial line in the left-right direction in the figure, and the piston 60 extends in the axial direction from the center of the end surface and protrudes outward (right side in the figure) from the cover member 56 of the cylinder 52. The rod-shaped first piston rod portion 62 and the center of the end surface of the piston 60 opposite to the first piston rod portion 62 extend in the axial direction and protrude outward from the cover member 58 of the cylinder 52 (left side in the figure). A round rod-shaped second piston rod portion 64 is integrally formed.

  The piston 60 is provided such that the outer peripheral portion thereof slides on the inner peripheral surface 54a of the cylinder main body 54 of the cylinder 52 and can move in the axial direction (the left-right direction in the drawing). Further, the cylinder 52 has a first oil chamber 66 and a second oil chamber 68 partitioned by a piston 60 inside, and the first oil chamber 66 and the second oil chamber 68 are provided inside the first oil chamber 66 and the second oil chamber 68. Filled with hydraulic oil.

  In the solid interior of the piston 60, flow paths 70 and 72 communicating between the first oil chamber 66 and the second oil chamber 68 are formed in a direction parallel to the axis of the piston 60. A pair of relief valves (pressure regulating valves) such as the relief valves 18 and 20 (see FIG. 12) of the conventional hydraulic damper 2 (not shown) are disposed in the opposite directions in the middle of the flow paths 70 and 72, respectively. Arranged to work.

  The relief valve (not shown) closes the cross sections of the flow paths 70 and 72 so that the hydraulic oil does not flow when the hydraulic damper 50 in which the piston 60 does not move in the cylinder 52 is not operated. When the hydraulic damper 50 moving in the cylinder 52 is operated, if the pressure of the hydraulic oil in one of the first oil chamber 66 and the second oil chamber 68 exceeds a certain value, the flow paths 70 and 72 It has a function of opening one side and allowing hydraulic oil to flow from one oil chamber to the other oil chamber.

  Further, in the solid interior of the piston 60, flow passages 77 and 78 are formed which communicate with a first oil chamber 66 and a second oil chamber 68 in the cylinder 52, and an accumulator oil chamber 76 of a pressure accumulator 74 which will be described later. ing.

  A throttle (hydraulic pressure reducing means) such as an orifice (not shown) is provided in the middle of each of the two flow paths 77 sharing the same axis, and the hydraulic pressure reducing means is provided in the first oil chamber 66. The hydraulic oil in the accumulator oil chamber 76 when the damper 60 moves in the cylinder 52 due to an earthquake or the like by restricting the flow rate of the hydraulic oil from the second oil chamber 68 side to the flow path 78 and the accumulator oil chamber 76. Has a function of reducing the pressure of the hydraulic oil from the pressure of the hydraulic oil in the first oil chamber 66 and the second oil chamber 68.

  The accumulator oil chamber 76 of the pressurization type accumulator 74 and the flow paths 77 and 78 in the piston 60 communicate with the first oil chamber 66 and the second oil chamber 68 in the cylinder 52, and hydraulic oil is also provided in these. Needless to say, is filled.

  A pressure accumulator 74 is connected in series to the left end of the second piston rod portion 64 in the drawing.

  The pressure type accumulator 74 includes an accumulator piston 80 that divides a space formed therein into two spaces, an accumulator oil chamber 76 that is formed in one of the two divided spaces, and the other of the two spaces. The spring 82 (elastic member) is housed and presses the accumulator piston 80 toward the accumulator oil chamber 76.

  The pressurization type accumulator 74 has a function of absorbing expansion and contraction of hydraulic oil in the first oil chamber 66 and the second oil chamber 68 in the cylinder 52.

  For example, when the piston 60 moves in the cylinder 52 and the pressure of the hydraulic oil in one of the first oil chamber 66 and the second oil chamber 68 is reduced, the pressure is reduced to the oil chamber. By supplying the hydraulic oil from the accumulator oil chamber 74, it is possible to prevent the hydraulic oil from becoming insufficient and the first oil chamber 66 and the second oil chamber 68 from becoming negative pressure, thereby stabilizing the performance of the hydraulic damper 50. Be able to.

  The pressurization type accumulator 74 also has a function as a reserve tank for hydraulic oil. When the amount of hydraulic oil in the first oil chamber 66 or the second oil chamber 68 is insufficient due to oil leakage or the like, the accumulator is used. The hydraulic oil can be supplied from the oil chamber 76 to the oil chambers 66 and 68.

  The second piston rod portion 64 is slidably fitted in a fitting hole 58 a formed in the cover member 58 of the cylinder 52 while maintaining the sealed state in the second oil chamber 68. The tip portion protrudes further outward, and the pressure accumulator 74 is provided at the tip portion protruding outward as described above.

  The cover member 58 of the cylinder 52 is integrally provided with a right end portion of the cylindrical extension member 84 in the drawing. The extension member 84 accommodates therein a tip end portion projecting outward from the cover member 58 of the second piston rod portion 64 and a pressure accumulator 74, and the extension member 84 is disposed in the same direction as the axis of the cylinder 52. It is provided to extend the length.

  And the left end part in the figure of the length direction of the extending member 84 is closed, and a fixed joint member 88 for fixing the hydraulic damper 50 to the building structure is attached to the left end part. .

  The first piston rod portion 62 is slidably fitted in a fitting hole 56a formed in the cover member 56 of the cylinder 52 while maintaining a sealed state in the first oil chamber 66. The tip portion protrudes outside the member 56, and a male screw portion 62a is formed on the outer periphery of the tip portion.

  The hydraulic damper 50 according to the present embodiment is connected to a building structure (not shown) via fixed joint members 86 and 88 attached to both ends thereof.

  As shown in FIG. 2, the joint member 86 of the hydraulic damper 50 has a disc-shaped attachment portion 86 a having the same axis as the axis of the first piston rod portion 62, and a side surface of the attachment portion 86 a on the right side in the drawing. It is comprised by the flat-shaped fixing board part 86b provided integrally.

  A female thread portion 86c is formed on the attachment portion 86a of the joint member 86 from the left surface in the drawing to the middle in the thickness direction.

  The male screw portion 62a at the tip of the first piston rod portion 62 is screwed to the female screw portion 94a of the nut 94 at the center in the length direction, and then the female screw of the mounting portion 86a of the fixed joint member 86. The portion 86c is screwed, and the mounting portion 86a and the nut 94 are tightened so that the contact surfaces are pressed against each other, thereby removing the backlash of the screw connection so as not to loosen the screw. The joint member 86 is integrally fixed to the male screw portion 62a of the first piston rod portion 62.

  Further, a shaft hole is formed in the portion of the first piston rod portion 62 outside the cover member 56 so as to open to the outer peripheral surface, and a female screw portion 62b is formed in the inner peripheral portion of the shaft hole. ing. Further, the shaft hole in which the female thread portion 62b is formed is formed along the axial direction of the first piston rod portion 62, and passes through the flow path 92 whose both ends are bent at a right angle. One oil chamber 66 is communicated. The inside of the flow path 92 of the first piston rod portion 62 is also filled with hydraulic oil.

  The hydraulic damper 50 according to the present embodiment is located outside the cover member 56 of the cylinder 52 and inside the outer diameter of the cylinder body 54, that is, inside the covering member 96 described later, Oil quantity monitoring means) is provided so as to be easily detachable via the pair of first and second joints 102 and 110.

  As shown in FIG. 3, the first joint 102 is housed in a cylindrical first joint body 104 that is partially closed at both ends, and an internal space 105 provided inside the first joint body 104. A spherical member 106 that engages with the spherical recess 105a at the upper end of the inner space 105 and closes the upper end, and a spring that is housed in the inner space 105 and presses the sphere 106 toward the spherical recess 105a. 108 (elastic member).

  A lower end portion of the first joint body 104 in the axial direction (vertical direction in the drawing) is formed to protrude downward, and a male screw portion 104a is formed at the lower end portion. The first joint 102 is attached to the outer peripheral portion of the first piston rod portion 62 by fastening the male screw portion 104 a to the female screw portion 62 b formed in the first piston rod portion 62.

  As shown in FIG. 4, when the lower end of the second joint 110 is not attached to the upper end of the first joint 102, the sphere 106 pressed upward by the lower spring 108 is the first joint body. By engaging with a spherical recess 105 a formed at the upper end of the internal space 105, the upper end of the internal space 105 is closed to seal the internal space 105.

  The internal space 105 of the first joint main body 104 passes through the flow path 104b formed in the axial direction at the lower end portion thereof and the flow path 92 formed in the axial direction of the first piston rod section 62, and passes through the inside of the cylinder 52. It communicates with the first oil chamber 66 (see FIG. 2). For this reason, the internal space 105 is filled with hydraulic oil, and the pressure of the hydraulic oil inside the internal space 105 is the same as the pressure of the first oil chamber 66.

  As shown in FIG. 4, the second joint 110 has a second joint main body 112 formed in a cylindrical shape, and has an internal thread at the upper end in the axial direction (vertical direction in the figure). A screw hole in which 112a is formed is formed. A channel 118 communicating with the screw hole is formed below the screw hole in which the female screw portion 112a is formed.

  The pressure gauge 90 is attached to the second joint 110 by tightening the male thread 90b of the pressure gauge 90 to the female thread 112a. The shaft hole 90 a that communicates with an internal pressure detector (not shown) of the pressure gauge 90 communicates with the flow path 118 of the second joint 110.

  The lower end portion of the second joint 110 is formed in a concave shape whose inside is recessed from the lower end surface of the second joint main body 112 upward in the drawing of the axial portion.

  Further, a projection 114 extending downward in the figure is provided on the inner axis of the concave shape, and a channel 116 is formed on the axis of the projection 114. It communicates with the upper flow path 118.

  As shown in FIG. 3, the lower end portion of the second joint main body 112 in which the inner side of the lower end portion of the second joint 110 is formed in a concave shape covers the upper end portion of the first joint main body 104 of the first joint 102. The second joint 110 can be attached to or detached from the first joint 102.

  When the second joint 110 is attached to the first joint 102 so that the projection 114 of the second joint body 112 is in the upper end of the first joint body 104 (see FIG. 4), and is slidably fitted. At this time, the interior space 105 is kept in a sealed state by a seal member 107 (see FIG. 4).

  At that time, the protrusion 114 of the second joint 110 comes into contact with the upper surface of the sphere 106 in the internal space 105 and enters the fitting hole 104c while pushing it downward. Yes.

  Therefore, when the second joint 110 is attached to the first joint 102, as shown in FIG. 3, the upper surface of the sphere 106 is separated from the spherical recess 105a at the upper end of the internal space 105 of the first joint body 104. To do. In this case, since the tip structure (not shown) of the protruding portion 114 is formed so that the internal space 105 and the flow path 116 communicate with each other, the internal space 105 has the axial holes of the flow path 118 and the pressure gauge 90. It communicates with 90a.

  At this time, the shaft hole 90a of the pressure gauge 90 communicates with the first oil chamber 66 in the cylinder 52 through the flow path 92 of the first piston rod portion 62 (see FIG. 2). The pressure of the hydraulic oil in the oil chamber 66 can be directly detected.

  When the pressure gauge 90 is not attached to the hydraulic damper 50, as shown in FIG. 4, the first joint 102 and the second joint 110 are separated, and the pressure gauge 90 is attached to the second joint 110. When attaching the pressure gauge 90 to the hydraulic damper 50, it is only necessary to attach the second joint 110 to the first joint 102 as shown in FIG.

  Further, when the second joint 110 is attached to the first joint 102 as shown in FIG. 3, the locking mechanism (not shown) is operated in the locking direction so that the two are not separated from each other, and as shown in FIG. When removing the second joint 110 from the one joint 102, the lock mechanism is operated in a direction to release the lock operation.

  As shown in FIG. 1, a left end portion of the cylindrical covering member 96 in the drawing is provided on the outer peripheral portion of the cover member 58 of the cylinder 52. The covering member 96 is in contact with the right end surface of the extending member 84 at the left end surface in the length direction of the covering member 96, and the right end portion of the covering member 96 in the length direction of the attachment portion 86 a of the joint member 86. The outer peripheral surface is arranged at a distance from the central portion in the thickness direction.

  The covering member 96 is adapted to house the tip of the cylinder 52 and the first piston rod 62 and the pressure gauge 90 therein, so that the internal pressure gauge 90 can be attached and detached from the outside. The covering member 96 is provided with an opening 96a.

  In the hydraulic damper 50 according to the present embodiment, after a long period of time, hydraulic oil leaks from the first oil chamber 66, the second oil chamber 68, or the accumulator oil chamber 76 in the cylinder 52, and the oil amount of the entire damper is reduced. When it decreases, the amount of oil in the accumulator oil chamber 76 that supplies hydraulic oil to these oil chambers 66 and 68 decreases.

  When the amount of oil in the accumulator oil chamber 76 decreases, the spring 82 that presses the accumulator piston 80 of the pressurization type accumulator 74 toward the accumulator oil chamber 76 extends, and the elastic force of the spring 82 decreases. The pressure applied to the hydraulic oil in the accumulator oil chamber 76 is also reduced.

  Further, the accumulator oil chamber 76 communicates with the first oil chamber 66 and the second oil chamber 68 in the cylinder 52 through the flow path 77 provided with the throttle (not shown). When the hydraulic damper 50 that does not move in the 52 is not operating, the pressure of the hydraulic oil in the accumulator oil chamber 76 is the same as the pressure of the hydraulic oil in the first oil chamber 66 and the second oil chamber 68. When the pressure of the hydraulic oil in the accumulator oil chamber 76 is reduced, the pressure of the hydraulic oil in the first oil chamber 66 and the second oil chamber 68 is also reduced.

  For this reason, the amount of hydraulic oil in the second oil chamber 68 of the cylinder 52 and the accumulator oil chamber 76 is measured by attaching a pressure gauge 90 and measuring the pressure in the first oil chamber 66 that has become smaller due to oil leakage. Since fluctuations can also be discriminated, fluctuations in the amount of hydraulic oil in the hydraulic damper 50 can be easily detected from the outside, and the hydraulic damper 50 has sufficient oil quantity to perform its original function. Can be easily recognized from the outside.

  Since the pressure gauge 90 is provided in the hydraulic damper 50 in this manner, the pressure accumulator 74 of the hydraulic damper 50 does not need to be integrally provided with the rod-like member 30 unlike the accumulator 22 of the conventional hydraulic damper 2. The length of the hydraulic damper 50 can be shortened, and its weight can be reduced. For this reason, the manufacturing price of the hydraulic damper 50 can be reduced.

  Further, the pressure gauge 90 provided in the hydraulic damper 50 according to the present embodiment is provided in the outer peripheral portion outside the cover member 56 of the first piston rod portion 62, and thus is provided in the conventional hydraulic damper 40. Unlike the pressure gauge 42, the pressure gauge 90 is not provided so as to protrude outward in the radial direction of the outer peripheral portion of the cylinder 52, so that the pressure gauge 90 can be prevented from interfering with other members around the hydraulic damper 50. it can.

  Further, the pressure gauge 90 according to the present embodiment is provided on the outer peripheral portion outside the cover member 56 of the first piston rod portion 62, and a cylindrical covering member 96 is provided on the outer periphery of the cover member 58 of the cylinder 52. Since it can be provided, it is possible to prevent an increase in the dimension in the radial direction perpendicular to the length direction of the hydraulic damper 50, and the external appearance of the hydraulic damper 50 is simplified and the appearance is significantly impaired. This can be prevented.

  In addition, the pressure gauge 90 according to the present embodiment is easily detachably attached to the first piston rod portion 62 via the pair of first and second joints 102 and 110. Since it is not necessary to always connect, the hydraulic damper in which the piston 60 moves in the cylinder 52 is detected by attaching the pressure gauge 90 only when the hydraulic damper 50 in which the piston 60 does not move in the cylinder 52 is inactive. It is possible to prevent the pressure gauge 90 from being attached during 50 operations.

  For this reason, the pressure gauge 90 according to the present embodiment does not require the pressure gauge 90 and the second joint 110 to be attached except when pressure is detected. Interference with other members can be prevented.

  Further, since the pressure gauge 90 according to the present embodiment can be removed except when detecting the pressure, the pressure gauge 90 is damaged due to the pressure increase caused by the operation of the hydraulic damper 50, and its measurement accuracy and lifespan. Can be prevented from decreasing.

  Further, since the pressure gauge 90 according to the present embodiment can be attached only when the damper 60 is not in operation, in which the piston 60 does not move within the cylinder 52, a pressure that is detected with a small range of fluctuation can be used. , Can be enlarged and accurately detected on the display meter. For this reason, the measurement accuracy of the pressure of the hydraulic oil in the first oil chamber 66 by the pressure gauge 90 can be improved.

  According to the hydraulic damper 50 according to the first embodiment of the present invention, a change in the amount of hydraulic oil in the hydraulic damper 50 can be easily recognized from the outside, and the hydraulic damper 50 is greatly enlarged. It is possible to prevent the components from becoming heavy and expensive, interference of other components with other members around the hydraulic damper 50, and the appearance of the hydraulic damper 50 being significantly impaired. It is possible to prevent the oil amount monitoring means from being damaged and the life of the oil from being reduced, and to improve the measurement accuracy of the oil amount monitoring means when the hydraulic damper 50 is not in operation.

  FIG. 5 is a diagram that is referred to for explaining a vibration-damping hydraulic damper 120 according to the second embodiment of the present invention.

  As shown in FIG. 5, the hydraulic damper 120 according to the present embodiment is different from the first embodiment in that a pressure gauge 90 is detachably provided at the tip of the first piston rod portion 124. Are different.

  The pressure gauge 90 in the present embodiment is disposed outside the cover member 56 in the axial direction of the cylinder 52 and outside the cover member 134 but outside the cover member 134. It is arranged inside the outer diameter dimension of the.

  The male screw portion 124a of the first piston rod portion 124 is integrally fixed to a joint member 128 having a gap for providing the pressure gauge 90.

  That is, in FIG. 5, the joint member 128 of the hydraulic damper 120 includes a disk-shaped mounting portion 128a having the same axis as that of the first piston rod portion 124 in the drawing, and two on the right end surface in the drawing of the mounting portion 128a. It is comprised by the plate-shaped fixing board part 128b in which the front end surface was provided integrally.

  The mounting portion 128a of the joint member 128 is formed with an axial hole 128d that passes in the axial direction from the right side surface thereof, and the axial hole 128d extends from the left side surface in the drawing to the center of the thickness thereof. A female screw portion 128c is formed in the peripheral portion.

  Further, the fixing plate portion 128b of the joint member 128 penetrates in the plate thickness direction (perpendicular to the paper surface in the drawing) from the surface on the attachment portion 128a side to the central portion in the length direction (left and right direction in FIG. 5). A long hole-shaped opening 128e is formed.

  Further, a female thread portion 124b is formed at the right end portion in the axial direction of the first piston rod portion 124 from the front end surface thereof toward the inner side in the axial direction. The space inside the female thread portion 124b is the first piston rod portion. It is formed along the axial direction of the portion 124, and only the left end portion in the drawing passes through the flow path 132 bent at a right angle (in the radial direction) and communicates with the first oil chamber 66 in the cylinder 52. ing.

  Then, a pressure gauge 90 (oil amount monitoring means) and a pair of first and first pairs are formed in a gap formed by the semi-long hole-shaped opening 128e of the fixed plate portion 128b of the joint member 128 and the shaft hole 128d of the mounting portion 128a. The second joints 102 and 110 are arranged, and the male screw part 104 a of the first joint main body 104 of the first joint 102 is fastened and attached to the female screw part 124 b of the first piston rod part 124.

  For this reason, the shaft hole 90 a of the pressure gauge 90 communicates with the first oil chamber 66 in the cylinder 52.

  The covering member 134 in the present embodiment is the same as the covering member 96 except that the opening 96a for attaching / detaching the pressure gauge 90 is not formed in the covering member 96 in the first embodiment. It comes to have a configuration.

  Also with the hydraulic damper 120 according to the second embodiment of the present invention, the same effects as those of the hydraulic damper 50 according to the first embodiment can be obtained.

  FIGS. 6 and 7 are views referred to for explaining a vibration-damping hydraulic damper 140 according to the third embodiment of the present invention.

  As shown in FIG. 6, the hydraulic damper 140 according to the present embodiment is provided with a connecting member 148 at the distal end portion of the first piston rod portion 144 extending to the right in the drawing of the piston 142, and the outer periphery of the connecting member 148. This embodiment is different from the first embodiment in that a pressure gauge 90 (oil amount monitoring means) is detachably provided in the part.

  Although the pressure gauge 90 in the present embodiment is disposed outside the cover member 56 in the axial direction of the cylinder 52 and outside the right end in the drawing of the covering member 134, the outer diameter of the cylinder 52 is arranged. It is designed to be placed on the inside.

  In the hydraulic damper 140 according to the present embodiment, as shown in FIG. 6, a ball joint 156 is attached to the distal end portion of the first piston rod portion 144 via a connecting member 148. A ball joint 158 is attached to the left end of the extension member 84 in the axial direction of the drawing.

  The connecting member 148 has the same axis as the axis of the first piston rod portion 144, and is formed in a columnar shape with a short length. As shown in FIG. 7, a female thread portion 148 a is formed at the left end portion of the connecting member 148 from the left end surface inward in the axial direction, and the right end portion of the connecting member 148 is axially extended from the right end surface. An internal thread portion 148c is formed inward.

  Then, a female thread portion 148b is formed on the outer peripheral surface of the connecting member 148 so that the male thread portion 104a of the first joint body 104 of the first joint 102 is screwed to the female thread portion 148b. A pressure gauge 90 is attached to the outer periphery of the connecting member 148 via a pair of first and second joints 102 and 110.

  Similar to the hydraulic damper 50 according to the first embodiment, the nut 94 and the connecting member 148 are screwed to the male screw portion 144a of the first piston rod portion 144, so that they are the first piston rod portion. 144 is integrally fixed to the front end portion of 144.

  Further, the male screw portion 156a of the ball joint 156 is fixed integrally with each other by being screwed to the female screw portion 148c of the connecting member 148.

  Further, the pressure gauge 90 in the present embodiment is formed along the flow path 152 bent at a right angle in the middle of the axis of the connecting member 148 and the axial direction of the first piston rod portion 124, and only the left end portion in the drawing. Is communicated with the first oil chamber 66 in the cylinder 52 through a flow path 154 bent at a right angle.

  Also with the hydraulic damper 140 according to the third embodiment of the present invention, the same effect as that of the hydraulic damper 50 according to the first embodiment can be obtained.

  FIG. 8 is a diagram that is referred to for explaining a vibration-damping hydraulic damper 160 according to the fourth embodiment of the present invention.

  As shown in FIG. 8, the hydraulic damper 160 according to the present embodiment is provided with a pressure gauge 90 (oil amount monitoring means) detachably provided on the right side of the cover member 168 of the cylinder 52 in the drawing. This is different from the first embodiment.

  Further, the pressure gauge 90 in the present embodiment is disposed in parallel with the axial direction of the cylinder 52, passes through the flow path 172 that penetrates the cover member 168, and communicates with the first oil chamber 66 in the cylinder 52. It has become.

  Further, the piston 162 in the present embodiment is the same as the piston 60 in the first embodiment except that the female thread portion 62b (see FIG. 2) of the first piston rod portion 62 and the flow path 92 are not formed. The same configuration as the piston 60 is provided, and the male screw portion 164a is formed in the first piston rod portion 164 in the same manner as the male screw portion 62a of the first piston rod portion 62.

  The cover member 168 in the present embodiment has the same configuration as the cover member 56 in the first embodiment except that the female screw portion 168b and the flow path 172 are formed. The fitting hole 168a is formed in the same manner as the fitting hole 56a.

  Also with the hydraulic damper 160 according to the fourth embodiment of the present invention, the same effects as those of the hydraulic damper 50 according to the first embodiment can be obtained.

  Further, in the hydraulic damper 160 according to the present embodiment, as compared with the case where the pressure gauge 90 is provided in the first piston rod portion 62 as in the hydraulic damper 50 according to the first embodiment, the pressure gauge Since the total length of the flow path between 90 and the first oil chamber 66 in the cylinder 52 can be shortened, the responsiveness of the pressure gauge 90 can be improved.

  FIG. 9 is a diagram that is referred to for explaining a vibration-damping hydraulic damper 180 according to the fifth embodiment of the present invention.

  As shown in FIG. 9, the hydraulic damper 180 according to the present embodiment can be attached and detached with an oil amount monitoring means 182 via first and second joints 102 and 110 provided on the outer periphery of the first piston rod 62. The second embodiment is different from the first embodiment in that the first embodiment is provided.

  The oil amount monitoring means 182 in the present embodiment includes a mounting member 184 formed in a cylindrical shape having a flange portion 184b, and an upper and lower portion in the figure provided integrally with the upper surface portion of the flange portion 184b of the mounting member 184. And a bellows 186 (a bellows cylindrical member) formed in a bellows cylindrical shape having a direction axis.

  The attachment member 184 of the oil amount monitoring means 182 is formed in a cylindrical shape on the lower end side, and a male screw portion 184a is formed on the outer periphery thereof. By tightening the male threaded portion 184a of the mounting member 184 to the female threaded portion 112a of the second joint main body 112, the oil amount monitoring means 182 is attached to the second joint 110, which is shown in FIG. 2 in the first embodiment. It is designed to be attached at the same position as the pressure gauge 90 shown.

  The bellows 186 of the oil amount monitoring means 182 is made of a thin metal, and is formed in a bellows cylindrical shape in which the cross-sectional shape of the outer peripheral cylindrical portion repeats unevenness in the axial direction (vertical direction in the figure). The upper end portion in the axial direction is closed by the tip surface 186a. The bellows 186 is elastically deformed in the axial direction so as to expand and contract in the same direction.

  The mounting member 184 and the bellows 186 are integrally fixed to each other by welding the vicinity of the contact portion in a state where the flange portion 184b of the mounting member 184 and the opening lower end portion of the bellows 186 are in contact with each other. It has become. Thereby, the space inside them becomes the 3rd oil chamber 188, and the inside is filled with hydraulic oil.

  The third oil chamber 188 passes through the flow path 190 formed in the axial portion of the mounting member 184 and the flow path 92 of the first piston rod portion 62 shown in FIG. The hydraulic oil pressure in the third oil chamber 188 is the same as the hydraulic oil pressure in the first oil chamber 66.

  The oil amount monitoring means 182 in the present embodiment is configured such that the bellows 186 expands and contracts in accordance with the pressure of the hydraulic oil in the first oil chamber 66, so that the operation in the first oil chamber 66 is performed. When the oil is reduced to a low pressure, the length of the bellows 186 is correspondingly shortened, and the distance from the upper end surface of the second joint body 112 to the front end surface 186a of the bellows 186 is decreased. It has become.

  For this reason, the amount of hydraulic oil in the first oil chamber 66 and the second oil chamber 68 of the cylinder 52 is determined by visually recognizing a change in the distance from the upper end surface of the second joint body 112 of the front end surface 186a of the bellows 186. Therefore, it is possible to easily detect the fluctuation in the amount of hydraulic oil in the hydraulic damper 180 from the outside, and the oil quantity sufficient for the hydraulic damper 180 to perform its original function. Can be easily recognized from the outside.

  Also with the hydraulic damper 180 according to the fifth embodiment of the present invention, the same effect as that of the hydraulic damper 50 according to the first embodiment can be obtained.

  FIG. 10 is a diagram which is referred to for explaining a vibration-damping hydraulic damper 200 according to the sixth embodiment of the present invention.

  As shown in FIG. 10, the hydraulic damper 200 according to the present embodiment can be attached and detached with an oil amount monitoring means 202 via first and second joints 102 and 110 provided on the outer periphery of the first piston rod 62. The second embodiment is different from the first embodiment in that the first embodiment is provided.

  The oil amount monitoring means 202 in the present embodiment includes a plurality of members housed in a space formed inside a casing constituted by a cylindrical member 204 having a vertical axis in the figure and a lid member 206. It is comprised by.

  In other words, the oil amount monitoring means 202 has a piston 210 (third piston) housed in the above space divided into two spaces on both the upper and lower sides of the piston 210 and formed in a lower space. Four oil chambers 208, a spring 212 (elastic member) that is housed in an upper space and presses the piston 210 toward the fourth oil chamber 208, and a shaft portion of the piston 210 are integrally connected to each other, and a tip portion thereof. Is formed of a rod-like member 214 that protrudes outward from the lid member 206 and can change the amount of protrusion.

  The cylindrical member 204 of the oil amount monitoring unit 202 is formed in a cylindrical shape, and a male screw portion 204a is formed to protrude downward at the lower end portion in the axial direction (vertical direction in the drawing).

  By tightening the male thread portion 204a of the cylindrical member 204 to the female thread portion 112a of the second joint body 112, the oil amount monitoring means 202 is attached to the second joint 110, and FIG. 2 in the first embodiment. Are attached at the same position as the pressure gauge 90 shown in FIG.

  Further, the cylindrical member 204 is formed with a recess recessed downward from the upper end surface in the figure, and a female thread portion 204b is formed on the cylindrical inner peripheral surface of the recess. A space 204c having a length in the vertical direction is formed further below the lower end face of the female screw portion 204b. The diameter of the space 204c is smaller than the diameter of the thread of the female screw portion 204b in the concave portion in which the female screw portion 204b is formed.

  The lid member 206 of the oil amount monitoring means 202 is formed in a disk shape having a male screw portion 206a on the outer periphery thereof. The lid member 206 is formed with a through hole 206b through which the rod-shaped member 214 loosely passes.

  In the cylindrical member 204 and the lid member 206, the male screw portion 206 a of the lid member 206 is screwed into the female screw portion 204 b of the cylindrical member 204, and the lower end surface of the lid member 206 in the drawing is from the upper end surface of the cylindrical member 204. The recessed portions are fixed to each other while being in contact with the bottom dead end surface of the female screw portion 204b. Thereby, a space 204c in which the piston 210 and the like are accommodated is formed therein.

  The piston 210 of the oil amount monitoring means 202 is formed in a disk shape whose axial direction coincides with the axial direction (vertical direction in the figure) of the cylindrical member 204, and its outer peripheral surface is the inner periphery of the fourth oil chamber 208. It contacts the surface and slides in the axial direction (vertical direction in the figure).

  In the space 204c inside the cylindrical member 204 and the lid member 206 of the oil amount monitoring means 202, the space opposite to the lid member 206 with respect to the piston 210 is a fourth oil chamber 208, in which hydraulic oil is contained. Is filled.

  The fourth oil chamber 208 passes through the flow path 216 formed in the axial portion at the lower end thereof and the flow path 92 of the first piston rod section 62 shown in FIG. The hydraulic oil pressure in the fourth oil chamber 208 is the same as the hydraulic oil pressure in the first oil chamber 66.

  On the other hand, in the space 204c inside the cylindrical member 204 and the lid member 206, the space opposite to the fourth oil chamber 208 with respect to the piston 210 is a spring that expands and contracts in the axial direction (vertical direction in the figure) of the piston 210. 212 is arranged in a state where both ends thereof are compressed by contacting the lid member 206 and the piston 210 respectively. The spring 212 opposes the pressure of the hydraulic oil by pressing the piston 210 pressed by the hydraulic oil in the fourth oil chamber 208 from the opposite side of the fourth oil chamber 208.

  Further, a rod-like member 214 is integrally fixed to the axial core portion of the surface of the piston 210 on the side where the lower end portion of the spring 212 is in contact. The rod-shaped member 214 is formed in a round bar shape, and its tip portion loosely penetrates a through hole 206 b formed in the lid member 206 and protrudes outside the lid member 206.

  In the oil amount monitoring means 202 in this embodiment, the spring 212 is expanded and contracted according to the pressure of the hydraulic oil in the first oil chamber 66 of the cylinder 52, and the first oil chamber 66 When the hydraulic oil in the cylinder is reduced to a low pressure, the spring 212 is correspondingly lengthened, and the piston 210 and the rod-shaped member 214 are moved toward the fourth oil chamber 208 by the length of the spring 212 (see FIG. Therefore, the amount of protrusion of the tip of the rod-shaped member 214 to the outside from the lid member 206 is reduced.

  For this reason, the change in the amount of hydraulic oil in the first oil chamber 66 and the second oil chamber 68 of the cylinder 52 is observed by visually recognizing the change in the length dimension in which the tip of the rod-shaped member 214 protrudes from the lid member 206 to the outside. Therefore, it is possible to easily detect the amount of hydraulic oil of the hydraulic damper 200 from the outside, and whether the hydraulic damper 200 has an oil amount sufficient to perform its original function. It can be easily recognized from the outside.

  Also with the hydraulic damper 200 according to the sixth embodiment of the present invention, the same effect as that of the hydraulic damper 50 according to the first embodiment can be obtained.

  In the hydraulic dampers 50 and the like according to the first to sixth embodiments, the vibration damper for vibration control has been described, but the present invention is also applicable to other types of hydraulic dampers such as those for seismic isolation. be able to.

  Further, the cylinder 52 in the hydraulic damper 50 or the like according to the first to sixth embodiments is provided in a cylindrical shape, but may not be provided in a cylindrical shape, for example, provided in a rectangular tube shape. It may be done.

  Further, the pressurization type accumulator 74 in the hydraulic damper 50 or the like according to the first to sixth embodiments is provided in series with the second piston rod portion 64. However, the conventional hydraulic damper 2, 40 may be provided inside the second piston rod portion 64.

  Moreover, although the connection member 148 in the said 3rd Embodiment shown in FIG. 6 was formed in the column shape, it is not necessary to be limited to a column shape, The ball joint 156, the 1st piston rod part 144, and pressure Any other shape such as a cube may be used as long as the gauge 90 can be attached.

  Further, by appropriately combining the configurations of the hydraulic dampers 50 and the like according to the first to sixth embodiments, the configurations of these hydraulic dampers may be different.

2 Hydraulic damper 4 Cylinder 4a, 4b End face 6 Piston 6a, 6b End face 8, 10 Oil chamber 12, 14 Piston rod 16 Extension member 16a Through hole 18, 20 Relief valve 22 Accumulator 24 Accumulator oil chamber 26 Accumulator piston 28 Spring 30 Rod-shaped member 40 Hydraulic damper 42 Pressure gauge 44 Flow path 50 Hydraulic damper 52 Cylinder 54 Cylinder body 54a Inner peripheral surface 56, 58 Cover member 56a, 58a Fitting hole 60 Piston 62 First piston rod portion 62a Male thread portion 62b Female thread portion 64 Second piston Rod portion 66 First oil chamber 68 Second oil chamber 70, 72 Flow path 74 Pressurization type accumulator 76 Accumulator oil chamber 77, 78 Flow path 80 Accumulator piston 82 Spring 84 Extension member 86 Joint member 86a Attached part 86b Fixed plate part 86c Female thread part 88 Joint member 90 Pressure gauge 90a Shaft hole 90b Male thread part 92 Channel 94 Nut 94a Female thread part 96 Cover member 96a Opening part 102 First joint 104 First joint body 104a Male thread part 104b Channel 104c Fitting hole 105 Internal space 105a Spherical recess 106 Spherical body 107 Seal member 108 Spring 110 Second joint 112 Second joint body 112a Female thread part 114 Projection part 116, 118 Flow path 120 Hydraulic damper 122 Piston 124 First piston rod part 124a Male thread Portion 124b Female thread portion 128 Joint member 128a Mounting portion 128b Fixing plate portion 128c Female thread portion 128d Shaft hole 128e Opening portion 132 Channel 134 Cover member 140 Hydraulic damper 142 Piston 144 First piston Rod part 144a Male thread part 148 Connecting member 148a, 148b, 148c Female thread part 152, 154 Flow path 156 Ball joint 156a Male thread part 158 Ball joint 160 Hydraulic damper 162 Piston 164 First piston rod part 164a Male thread part 168 Cover member 168a Fitting hole 168b Female thread portion 172 Flow path 180 Hydraulic damper 182 Oil amount monitoring means 184 Mounting member 184a Male thread portion 184b Flange portion 186 Bellows 186a Tip surface 188 Third oil chamber 190 Flow path 200 Hydraulic damper 202 Oil amount monitoring means 204 Cylindrical member 204a Male screw Portion 204b female screw portion 204c space 206 lid member 206a male screw portion 206b through hole 208 fourth oil chamber 210 piston 212 spring 214 rod-shaped member 216 flow path

Claims (8)

A cylinder formed in a cylindrical shape closed at both ends;
A piston having a first piston rod portion, and a second piston rod portion projecting from each of both axial ends of the cylinder housed in the cylinder on the outside of the cylinder,
Two oil chambers formed on both sides in the axial direction of the piston in the cylinder and filled with hydraulic oil inside;
An accumulator having an accumulator oil chamber provided in the second piston rod portion and communicating with two oil chambers in the cylinder through a flow path;
In the outer peripheral portion of the first piston rod part, axially outward from an end portion of said cylinder, and detachably provided radially inward of the cylinder, without passing through the accumulator oil chamber, wherein in said cylinder 2 Oil amount monitoring means communicating with one of the oil chambers on the first piston rod portion side through a flow path formed in the first piston rod portion ;
A hydraulic damper comprising: an opening that allows the oil amount monitoring means to be detachable from the outside; and a covering member that is provided so as to cover an outer peripheral surface of the cylinder and the first piston rod portion. . A cylinder formed in a cylindrical shape closed at both ends;
A piston having a first piston rod portion and a second piston rod portion that are housed in the cylinder and project from the both ends in the axial direction of the cylinder to the outside of the cylinder;
Two oil chambers formed on both sides in the axial direction of the piston in the cylinder and filled with hydraulic oil inside;
An accumulator having an accumulator oil chamber provided in the second piston rod portion and communicating with two oil chambers in the cylinder through a flow path;
One end is connected to the tip of the first piston rod part, and the mounting part has an axial hole penetrating in the axial direction of the first piston rod part,
A fixed plate portion that is connected to the other end portion of the attachment portion, opens to the attachment portion side, and has an opening that penetrates in the plate thickness direction;
The shaft hole of the mounting portion and the opening of the fixing plate portion are disposed in a gap formed on the outer side in the axial direction than the end portion of the cylinder and on the inner side in the radial direction of the cylinder. Detachably provided at the tip of the first piston rod part inserted halfway in the axial direction of the shaft hole of the part, and the second of the two oil chambers in the cylinder without the interposition of the accumulator oil chamber. An oil amount monitoring means that communicates with one side of the first piston rod portion through a flow path formed in the first piston rod portion;
A hydraulic damper comprising: a covering member provided so as to cover an outer peripheral surface of the cylinder and the first piston rod portion . A cylinder formed in a cylindrical shape closed at both ends;
A piston having a first piston rod portion and a second piston rod portion that are housed in the cylinder and project from the both ends in the axial direction of the cylinder to the outside of the cylinder;
Two oil chambers formed on both sides in the axial direction of the piston in the cylinder and filled with hydraulic oil inside;
An accumulator having an accumulator oil chamber provided in the second piston rod portion and communicating with two oil chambers in the cylinder through a flow path;
A connecting member having one end connected to the tip of the first piston rod portion and the other end connected to a ball joint;
It is disposed on the outer side in the axial direction from the end of the cylinder and on the inner side in the radial direction of the cylinder, and is detachably provided on the outer peripheral part of the connecting member, and without the accumulator oil chamber, Oil amount monitoring means communicating with one of the two oil chambers on the first piston rod portion side through flow paths respectively formed in the first piston rod portion and the connecting member;
A hydraulic damper comprising: a covering member provided so as to cover an outer peripheral surface of the cylinder and the first piston rod portion . A cylinder formed in a cylindrical shape closed at both ends;
A piston having a first piston rod portion and a second piston rod portion that are housed in the cylinder and project from the both ends in the axial direction of the cylinder to the outside of the cylinder;
Two oil chambers formed on both sides in the axial direction of the piston in the cylinder and filled with hydraulic oil inside;
An accumulator having an accumulator oil chamber provided in the second piston rod portion and communicating with two oil chambers in the cylinder through a flow path;
A fitting hole penetrating in the axial direction of the first piston rod portion through which the first piston rod portion is inserted, and closing an end portion of the cylinder on the first piston rod portion side; and the first piston rod A cover member formed with a flow path penetrating in the axial direction of the portion;
The two oils in the cylinders are disposed on the outer side in the axial direction from the ends of the cylinders and on the inner side in the radial direction of the cylinders, and are detachably attached to the cover member without interposing the accumulator oil chamber. An oil amount monitoring means communicating with one of the first piston rod part side of the chamber through the flow path of the cover member;
A hydraulic damper comprising: an opening that allows the oil amount monitoring means to be detachable from the outside; and a covering member that is provided so as to cover an outer peripheral surface of the cylinder and the first piston rod portion. . The hydraulic damper according to any one of claims 1 to 4 , wherein the oil amount monitoring means is detachably provided through connection / separation of a pair of joint members. The hydraulic damper according to any one of claims 1 to 5 , wherein the oil amount monitoring means includes a pressure gauge that detects a pressure of hydraulic oil in the oil chamber. The hydraulic damper according to any one of claims 1 to 5 , wherein the oil amount monitoring means includes a bellows cylindrical member that expands and contracts in its axial direction in accordance with the pressure of hydraulic oil in the oil chamber. . The oil amount monitoring means is
A housing having a space inside,
A third oil chamber that is housed in the space and that divides the space into two spaces and communicates with one of the two oil chambers on the first piston rod side is formed in one of the two spaces. A third piston;
An elastic member housed in the other of the two spaces so as to press the third piston toward the third oil chamber;
A rod-shaped member provided integrally with the third piston and capable of projecting to the outside of the housing;
Any one of claims 1 to 5, characterized in that the amount of projection of the outside of the housing of the rod-shaped member in accordance with a variation in one of the pressure of the hydraulic oil of the two oil chambers was made to vary Hydraulic damper as described in

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