JP7112852B2 - Regulator and hydraulic damper - Google Patents

Description

The present invention relates to a pressure regulating valve and a hydraulic damper using the same.

Conventionally, hydraulic dampers have been used in braces and the like in order to reduce shaking of buildings due to earthquakes, wind, and the like. Hydraulic dampers use the fluid resistance of oil to generate a resistance (damping force) against the shaking of buildings, absorb the shaking of buildings, and improve earthquake resistance and livability.

Such a hydraulic damper is composed of, for example, a cylinder filled with hydraulic oil and a piston that divides the cylinder into two hydraulic chambers. As shown in Japanese Unexamined Patent Application Publication No. 2002-100000, there is a pressure regulating valve provided in a flow path connecting both hydraulic chambers.

Japanese Patent Application Laid-Open No. 2006-349021

Generally, it is desirable that the hydraulic damper has a linear damping coefficient, which is the relationship between the displacement speed of the piston and the generated damping force. Therefore, it is necessary to use a pressure regulating valve with excellent linearity.

On the other hand, in a seismic isolation structure using a hydraulic damper, when an unexpected earthquake occurs, there is a risk that the displacement will become larger than expected and the structure will be damaged. Therefore, when the displacement speed exceeds a predetermined value, it is required to increase the damping force abruptly. However, in the conventional hydraulic damper, there is a problem that the structure becomes complicated, such as combining a plurality of pressure regulating valves, when trying to give the two-stage damping characteristic.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-described problems, and provides a pressure regulating valve and a hydraulic damper that have a simple structure and have the performance of greatly increasing the load generated when the displacement speed exceeds a predetermined value. for the purpose.

In order to achieve the above object, a first invention comprises a valve body, a valve body holding portion having a hole through which the valve body passes, and a spring for pressing the valve body against the valve body holding portion, The valve body is provided with a first valve part provided on the base side and a second valve part provided on the tip side, separated from each other. When the pressure on the side of the second valve portion becomes equal to or higher than a predetermined value with respect to the valve pressing portion, the valve body moves against the spring, Fluid flows through the hole from the side of the second valve portion to the side of the first valve portion, and as the amount of movement of the valve body increases, the cross-sectional area through which the fluid flows between the hole and the first valve portion increases. Further, when the valve body moves against the spring, the cross-sectional area between the hole and the second valve portion is larger than the cross-sectional area through which the fluid flows between the hole and the first valve portion as the amount of movement increases. The pressure regulating valve is characterized in that the cross-sectional area through which the fluid flows between is small.

The second valve portion may have a hole through which the fluid can pass, or a groove through which the fluid can pass.

According to the first invention, the first valve portion and the second valve portion are integrally formed in the valve body, and as the amount of movement increases, the inflow cross-sectional area in the first valve portion increases, and the valve body further moves. Then, as the amount of movement increases, the inflow cross-sectional area of the second valve portion decreases. Therefore, two stages of damping force can be exhibited by one pressure regulating valve.

In this case, for the structure of the first valve portion, a poppet valve type valve shape or a spool valve type valve shape used in conventional pressure regulating valves can be applied.

A second invention comprises a pressure regulating valve according to the first invention, a cylinder, and a piston that divides the cylinder into hydraulic chambers and is movably provided in the cylinder, wherein the pressure regulating valve is and a hydraulic damper provided in a flow path connecting the hydraulic chambers.

According to the second aspect of the invention, when the displacement speed increases and the first valve portion opens more than the predetermined value, the second valve portion closes. Therefore, when the displacement speed exceeds the predetermined value, the damping force is rapidly increased. It is possible to obtain a hydraulic damper that can

According to the present invention, it is possible to provide a pressure regulating valve and a hydraulic damper that have a simple structure and have the performance of greatly increasing the generated load when the displacement speed exceeds a predetermined value.

FIG. 2 is a diagram showing the structure of the hydraulic damper 1; Sectional drawing which shows the pressure regulation valve 11. FIG. (a), (b) is a figure which shows the operation|movement of the pressure regulating valve 11. FIG. (a) is a cross-sectional view showing a pressure regulating valve 11a, and (b) is a view in the direction of arrow K in (a). (a) is a cross-sectional view showing a pressure regulating valve 11b, and (b) is a view in the direction of arrow L in (a). (a) is a cross-sectional view showing the pressure regulating valve 11c, and (b) is a cross-sectional view taken along line MM of (a). (a) is a cross-sectional view showing a pressure regulating valve 11d, and (b) is a cross-sectional view showing a pressure regulating valve 11e.

Hereinafter, the hydraulic damper of the present invention will be described in detail with reference to the drawings. FIG. 1 is a diagram showing the structure of a hydraulic damper 1. FIG. The hydraulic damper 1 mainly includes a cylinder 3, a piston 5, piston rods 7a and 7b, a pressure regulating valve 11, and the like. Note that the structure of the hydraulic damper is not limited to the illustrated example. Also, the structure of the accumulator and the like is omitted from the drawing.

A piston 5 is movably provided in the cylindrical cylinder 3 . Both sides of the piston 5 are provided with cylindrical piston rods 7a and 7b. A joint 13a is connected to the piston rod 7b. A joint 13 b is connected to the cylinder 3 . The joints 13a and 13b are fixed to braces or bases of the building.

The inside of the cylinder 3 is divided by the piston 5 into a hydraulic chamber 9a and a hydraulic chamber 9b. The hydraulic chambers 9a and 9b are filled with working oil. The piston 5 is provided with a pair of flow paths connecting the hydraulic chambers 9a and 9b. Pressure regulating valves 11 are arranged in the respective flow paths in opposite directions. The opening of the pressure regulating valve 11 changes according to the pressure difference between the hydraulic chambers. The details of the structure of the pressure regulating valve 11 will be described later.

Next, operation of the hydraulic damper 1 will be described in detail with reference to FIG. FIG. 1 shows a case where a force such as an earthquake or wind acts on a building and an external force acts on the piston 5 . When the piston 5 moves in the A direction, the working oil filled in the hydraulic chamber 9a is compressed. The hydraulic oil compressed in the hydraulic chamber 9a flows into one (upper in the figure) pressure regulating valve 11 (arrow C in the figure).

When hydraulic fluid having a predetermined pressure or more flows into the pressure regulating valve 11, the pressure regulating valve 11 opens, and the hydraulic fluid flows into the hydraulic chamber 9b via the pressure regulating valve 11 (arrow D in the drawing). In this manner, by adjusting the spring or the like provided in the pressure regulating valve 11 with respect to the speed at which the piston 5 moves in the A direction, a damping force is generated in the piston 5 in a direction that cancels out the force in the A direction.

Next, a case where the directions of the forces acting on the building, such as an earthquake and wind, are reversed will be described. When the piston 5 moves in the B direction, the working oil filled in the hydraulic chamber 9b is compressed. The hydraulic oil compressed in the hydraulic chamber 9b flows into the other (lower in the figure) pressure regulating valve 11 (arrow E in the figure).

When hydraulic fluid having a predetermined pressure or more flows into the pressure regulating valve 11, the pressure regulating valve 11 opens, and the hydraulic fluid flows into the hydraulic chamber 9a via the pressure regulating valve 11 (arrow F in the drawing). In this manner, by adjusting the spring or the like provided in the pressure regulating valve 11 with respect to the speed at which the piston 5 moves in the B direction, a damping force is generated in the piston 5 in a direction that cancels out the force in the B direction.

Next, the pressure regulating valve 11 will be described in detail. FIG. 2 is a cross-sectional view showing the structure of the pressure regulating valve 11. As shown in FIG. The pressure regulating valve 11 is composed of a sleeve 15, a valve pressing portion 18, a valve body 19, a spring 21, and the like. A spring retainer 23 is arranged on the rear end side (left side in the drawing) of the cylindrical sleeve 15, and a valve body holding portion 18 is arranged on the front end side (right side in the drawing).

The valve body pressing portion 18 and the spring pressing portion 23 are provided with holes 17a and 17b through which hydraulic oil flows, respectively. A spring 21 and a valve element 19 are provided inside the sleeve 15 and between the spring retainer 23 and the valve element pressing portion 18 .

The valve body 19 has a first valve portion 25 provided on the base side (rear end side of the sleeve 15) and a second valve portion 27 provided on the tip side. The first valve portion 25 has a poppet valve type valve shape. The second valve portion 27 has a disc shape with an outer diameter larger than that of the hole 17a. The first valve portion 25 and the second valve portion 27 are separated from each other via a rod-shaped connecting portion 29 . The connecting portion 29 penetrates through the hole 17 a of the valve body pressing portion 18 . Therefore, the valve body pressing portion 18 is arranged between the first valve portion 25 and the second valve portion 27 .

The valve body 19 is pressed forward toward the valve body pressing portion 18 by a spring 21 . In a state where the first valve portion 25 is pressed against the valve body pressing portion 18 by the spring 21 , the hole 17 a is closed by the first valve portion 25 . That is, hydraulic oil does not flow into the sleeve 15 through the hole 17a.

Next, operation of the pressure regulating valve 11 will be described. FIG. 3(a) shows a state in which the valve body 19 has moved rearward (to the left in the drawing) from the normal state against the force of the spring 21 due to the pressure of the hydraulic fluid. When the valve body 19 moves backward against the spring 21 , a gap is formed between the first valve portion 25 and the valve body pressing portion 18 . Therefore, hydraulic oil flows into the sleeve 15 through the hole 17a (in the direction of arrow I in the figure). At this time, when the displacement speed of the piston increases, the amount of movement of the valve body 19 increases. increases.

Here, the length of the connecting portion 29 is sufficiently longer than the length of the valve body pressing portion 18 . Therefore, there is a sufficient space between the second valve portion 27 and the valve body pressing portion 18 . Therefore, in the initial stage when the valve body 19 starts to move against the spring 21, the inflow cross-sectional area of the second valve portion 27 ( Middle H part) is sufficiently large. Therefore, the damping force is determined by the resistance (I in the drawing) of hydraulic oil flowing between the first valve portion 25 and the valve body pressing portion 18 (hole 17a). At this time, the displacement speed of the piston 5 (the flow rate of hydraulic oil) and the damping force are linear.

As shown in FIG. 3B, when the displacement speed of the piston 5 further increases and the valve body 19 moves backward against the spring 21, the distance between the hole 17a and the second valve portion increases as the amount of movement increases. The inflow cross-sectional area between When the valve body 19 moves more than a predetermined amount, the valve body holding part 18 (hole 17a) and the valve body holding part 18 (hole 17a) are larger than the inflow cross-sectional area (G part in the figure) between the valve body holding part 18 (hole 17a) and the first valve part 25. The inflow cross-sectional area (H portion in the drawing) between the second valve portion 27 and the second valve portion 27 becomes smaller. Therefore, the damping force is determined by the resistance (J in the figure) of hydraulic oil flowing between the second valve portion 27 and the valve body pressing portion 18 (hole 17a).

That is, if the displacement speed is equal to or less than a predetermined value, the damping force is determined by the resistance (I in the figure) of hydraulic oil flowing between the first valve portion 25 and the valve body pressing portion 18 (hole 17a), and the displacement speed becomes a predetermined value or more, it is determined by the resistance (J in the figure) of hydraulic oil flowing between the second valve portion 27 and the valve body pressing portion 18 (hole 17a). At this time, the inflow cross-sectional area between the second valve portion 27 and the valve body pressing portion 18 (hole 17a) decreases as the displacement speed increases and the amount of movement of the valve body 19 increases. Therefore, when the displacement side exceeds a predetermined value, the damping force can be rapidly increased.

As described above, according to the present embodiment, the inflow cross-sectional area between the valve body pressing portion 18 (hole 17a) and the first valve portion 25 is equal to that of the valve body pressing portion 18 (hole 17a) and the second valve portion. 27, the inflow cross-sectional area increases as the amount of movement of the valve body 19 increases. When the inflow cross-sectional area between the valve body pressing portion 18 (hole 17a) and the second valve portion 27 becomes smaller than the inflow cross-sectional area between area is reduced.

That is, when the displacement speed (flow rate of hydraulic oil) of the piston 5 is below a predetermined value, the single pressure regulating valve 11 linearly increases the damping force with respect to the increase in the displacement speed (flow rate of hydraulic oil). When the displacement speed (flow rate of hydraulic oil) reaches or exceeds a predetermined value, the damping force can be rapidly increased. Therefore, even if an unexpected earthquake occurs, the hydraulic damper with a simple structure can prevent the displacement from becoming larger than expected, and can prevent the structure from being damaged.

Next, a second embodiment will be described. 4(a) is a cross-sectional view of the pressure regulating valve 11a, and FIG. 4(b) is a view in the direction of arrow K in FIG. 4(a). In the following description, the same reference numerals as in FIG. 2 are assigned to the components having the same functions as those of the pressure regulating valve 11, and overlapping descriptions are omitted.

The pressure regulating valve 11a has substantially the same configuration as the pressure regulating valve 11, but the structure of the second valve portion 27 of the valve body 19 is different. In this embodiment, a plurality of holes 31 are formed in the second valve portion 27 . The outer peripheral surface of the second valve portion 27 is guided by the inner surface of the flow path. Hydraulic oil passes through the second valve portion 27 through the hole 31 and flows into the hole 17a.

As shown in FIG. 4B, the center position of the hole 31 in the radial direction of the second valve portion 27 is arranged outside the hole 17a. In the illustrated example, the hole 31 and the hole 17a do not overlap in the K arrow view, but a part of the hole 31 may overlap the hole 17a. When the valve body 19 moves and the distance between the second valve part 27 and the valve body pressing part 18 becomes shorter, the distance between the hole 31 and the end surface of the valve body pressing part 18 becomes shorter, and the inflow cross-sectional area decreases. . Therefore, when the displacement speed of the piston 5 (the flow rate of hydraulic oil) reaches or exceeds a predetermined value, the damping force can be rapidly increased.

According to the pressure regulating valve 11a of the second embodiment, the same effect as the pressure regulating valve 11 can be obtained. Further, the second valve portion 27 can be guided by moving the second valve portion 27 along the inner wall of the flow path.

Next, a third embodiment will be described. 5(a) is a cross-sectional view of the pressure regulating valve 11b, and FIG. 5(b) is a view in the direction of arrow L in FIG. 5(a). The pressure regulating valve 11b has substantially the same configuration as the pressure regulating valve 11a, but the structure of the second valve portion 27 of the valve body 19 is different. In this embodiment, a plurality of grooves 33 are formed in the second valve portion 27 . In the illustrated example, the groove 33 and the hole 17a do not overlap in the L arrow view, but a part of the groove 33 may overlap the hole 17a. The outer peripheral surface of the second valve portion 27 is guided by the inner surface of the flow path. Hydraulic oil passes through the second valve portion 27 through the groove 33 and flows into the hole 17a.

According to the third embodiment, effects similar to those of the second embodiment can be obtained. As described above, the second valve portion 27 may take any form as long as the inflow cross-sectional area becomes smaller as the amount of movement of the valve body 19 increases.

Next, a fourth embodiment will be described. 6(a) is a cross-sectional view of the pressure regulating valve 11c, and FIG. 6(b) is a cross-sectional view taken along line MM of FIG. 6(a). The pressure regulating valve 11c has substantially the same configuration as the pressure regulating valve 11, but the structure of the first valve portion 25 of the valve body 19 is different. In this embodiment, the first valve portion 25 has a valve shape of a spool valve type.

The tip of the first valve portion 25 is inserted into the hole 17 a of the valve body pressing portion 18 . A connecting portion 29 is provided at the tip of the first valve portion 25 inserted into the hole 17 a , and the second valve portion 27 is arranged at the tip of the connecting portion 29 . A notch-shaped groove 35 is provided at the tip of the first valve portion 25 in the hole 17a. The groove 35 serves as a flow path for hydraulic oil. The depth of the groove 35 gradually increases from the tip side toward the base side.

When the valve body 19 moves, the tip of the first valve portion 25 moves along the hole 17a. At this time, hydraulic oil flows into the sleeve 15 through the gap between the groove 35 and the hole 17a. As the amount of movement of the valve body 19 increases, the gap between the end of the valve body pressing portion 18 (hole 17a) and the groove 35 increases, so that the inflow cross-sectional area of the hydraulic oil increases. On the other hand, when the amount of movement of the valve body 19 exceeds the predetermined amount, the inflow cross-sectional area between the second valve portion 27 and the valve body pressing portion 18 becomes smaller. Therefore, when the displacement speed of the piston 5 (the flow rate of hydraulic oil) reaches or exceeds a predetermined value, the damping force can be rapidly increased.

The shape of the second valve portion 27 is not limited to the example shown in FIG. 6(a). For example, like a pressure regulating valve 11d shown in FIG. 7A, the rear surface of the second valve portion 27 (connecting portion 29 side) may be tapered linearly so that the diameter decreases toward the connecting portion 29 side. Further, like the pressure regulating valve 11e shown in FIG. 7(b), the back surface of the second valve portion 27 may be formed into a curved tapered shape in which the diameter decreases toward the connecting portion 29 side.

According to the fourth embodiment, effects similar to those of the first embodiment can be obtained. As described above, the first valve portion 25 may take any form as long as the inflow cross-sectional area increases as the amount of movement of the valve body 19 increases.

Although the preferred embodiments of the hydraulic damper and the like according to the present invention have been described above with reference to the accompanying drawings, the present invention is not limited to such examples. It is obvious that a person skilled in the art can conceive of various modifications or modifications within the scope of the technical ideas disclosed in the present application, and these also belong to the technical scope of the present invention. Understood.

For example, the forms of the first valve portion 25 and the second valve portion 27 in each embodiment can be combined with each other.

1 Hydraulic damper 3 Cylinder 5 Piston 7a, 7b Piston rod 9a, 9b Hydraulic chamber 11, 11a, 11b, 11c, 11d, 11e Pressure regulating valve 13a, 13b …………Joint 15……Sleeve 17a, 17b……Hole 18……Valve body holding portion 19……Valve body 21……Spring 23……Spring holding member 25……First valve portion 27 ……Second valve portion 29 ……Connecting portion 31 ……Hole 33, 35 ……Groove

Claims (4)

a valve body;
a valve body holding portion having a hole through which the valve body passes;
a spring that presses the valve body against the valve body pressing portion;
and
The valve body is provided with a first valve part provided on the base side and a second valve part provided on the tip side, separated from each other. arranged between the second valve part,
When the pressure on the side of the second valve portion exceeds a predetermined level with respect to the valve pressing portion, the valve body moves against the spring to move from the side of the second valve portion to the side of the first valve portion. fluid flows through the hole, and as the amount of movement of the valve element increases, the cross-sectional area through which the fluid flows between the hole and the first valve portion increases;
Further, when the valve body moves against the spring, the cross-sectional area of the fluid flowing between the hole and the first valve portion is larger than that between the hole and the second valve portion as the amount of movement increases. A pressure regulating valve characterized in that a cross-sectional area through which fluid flows between is reduced. 2. The pressure regulating valve according to claim 1, wherein the second valve portion is formed with a plurality of holes through which fluid can pass. 2. The pressure regulating valve according to claim 1, wherein the second valve portion is formed with a plurality of grooves through which fluid can pass. a pressure regulating valve according to any one of claims 1 to 3;
a cylinder;
a piston that divides the cylinder into hydraulic chambers and is movably provided in the cylinder;
and
A hydraulic damper, wherein the pressure regulating valve is provided in a flow path connecting the hydraulic chambers.

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