JP6383656B2 - Vibration measuring instrument and fluid cylinder device - Google Patents

Description

  The present invention relates to a vibration measuring device and a fluid cylinder device.

  Damping devices (dampers) used in vibration control devices and seismic isolation devices cannot be switched according to the vibration level, so they are designed to exhibit a damping effect effectively for a specific vibration level. Will be. Therefore, the damping effect is not sufficiently exhibited except for the vibration level.

  For example, a design specification that effectively exhibits a damping effect during a large earthquake does not provide a sufficient damping effect during a small earthquake or strong wind. On the other hand, if the design specification is such that it effectively exhibits a damping effect during small earthquakes or strong winds, the damping effect will not be sufficiently achieved during a large earthquake.

Therefore, Patent Document 1 discloses a technique related to a variable damping device that controls damping characteristics of a damping device (damper) in multiple steps or continuously according to the vibration state of the structure. Specifically, based on the index I (damper state quantity) calculated by the function f = √ {X ² + (V / ω) ² } using the velocity signal V, the displacement signal X, and the constant value ω. Thus, an attenuation command value that defines the throttle amount of the electromagnetic proportional valve is calculated, and the throttle of the electromagnetic proportional valve is controlled using the calculated attenuation command value as a control signal.

  However, it is required to reduce or omit the calculation in the calculation device (computer) and control the variable attenuation device and the like more easily.

Japanese Patent No. 4621364

  In view of the above facts, an object of the present invention is to provide a vibration measuring device and a fluid cylinder device using the vibration measuring device that can reduce or omit the calculation in the calculating device.

  The vibration measuring instrument according to claim 1, wherein a cylinder portion in which a fluid is sealed, a partition wall that divides the inside of the cylinder portion into a first chamber and a second chamber in the axial direction and is displaced in the axial direction, and the cylinder portion An orifice that is provided on the first chamber and the second chamber and that changes in proportion to a value of a function using a displacement of the partition wall and a rated displacement. And an output part for outputting the pressure of the fluid in the first chamber and the second chamber, respectively.

  In the vibration measuring instrument according to the first aspect, when the partition wall is displaced in the axial direction in the cylindrical portion, the flow passage area of the orifice on the fluid inflow side flowing through the first chamber and the second chamber uses the displacement of the partition wall and the rated displacement. It changes so as to be proportional to the value of the function. A pressure is generated in the compression side chamber according to the displacement and speed of the partition wall, and the output unit outputs this pressure.

  Then, by using the output pressure as an index for controlling the damping force of the damping device provided in the building, for example, the calculation in the computing device for controlling the damping force is reduced or omitted.

The vibration measuring instrument according to claim 2 is K = √ {X0 ² −X ² }, where K is the function, X is the displacement of the partition wall, and X0 is the rated displacement of the partition wall.

  In the vibration measuring instrument according to the second aspect, when it is assumed that the partition wall vibrates with a sine wave having the amplitude X0 and the circular frequency ω, the pressure of the output portion becomes a constant value regardless of the displacement X.

  For example, if the damping force of the damping device is controlled using the output pressure as an index, stable control is performed in a steady state. Therefore, for example, it is possible to prevent the occurrence of an impact due to sudden switching of the damping force.

  The fluid cylinder device according to claim 3 is configured such that the piston moves in the axial direction in the cylinder in which the fluid is sealed, and the partition wall is displaced in proportion to the movement of the piston of the fluid cylinder body. The vibration measuring device according to claim 1 or 2 provided, and resistance changing means for changing a resistance characteristic of the fluid cylinder body by a pressure output from an output portion of the vibration measuring device.

  In the fluid cylinder device according to the third aspect, pressure is generated in the compression side chamber of the vibration measuring device, and the output unit outputs this pressure. Then, the resistance changing means changes the resistance characteristic of the fluid cylinder device by the output pressure. Therefore, the calculation in the calculation device for controlling the damping force is reduced or omitted. In addition, for example, by using this fluid cylinder device as a vibration damping device for a building, it is possible to prevent the occurrence of an impact due to abrupt switching of resistance characteristics.

  According to the present invention, it is possible to reduce or omit the calculation in the calculation device.

It is a block diagram which shows the system configuration | structure of the variable attenuation apparatus which concerns on 1st embodiment of this invention. It is a circuit diagram of a pressure circuit. It is a block diagram which shows typically the vibration measuring device used for the variable damping device. It is a block diagram which shows the system configuration | structure of the variable attenuation apparatus which concerns on 2nd embodiment of this invention. It is a block diagram which shows typically the basic composition of a vibration measuring device. (A) which shows the vibration measuring device of a 1st Example is a block diagram in the state in which a partition has an axial direction center, (B) is a top view which shows a groove | channel, (C) is an axial direction edge part. (D) is a sectional view taken along line 6D-6D in (A), and (E) is a sectional view taken along line 6E-6E in (C). (A) which shows the vibration measuring device of 2nd Example is a block diagram in the state which has a partition in the axial direction center, (B) is a top view which shows a groove | channel, (C) is an axial direction edge part. (D) is a sectional view taken along line 7D-7D in (A), and (E) is a sectional view taken along line 7E-7E in (C). (A) which shows the vibration measuring device of 3rd Example is a block diagram in the state which has a partition in the axial direction center, (B) is a top view which shows an orifice, (C) is 8C- of (A). It is sectional drawing along 8C line. (A) which shows the vibration measuring device of 4th Example is a block diagram of the state which has a partition in the axial direction center, (B) is a top view which shows an orifice, (C) is 9C- of (A). It is sectional drawing which followed the 9C line. It is a graph which shows the relationship between the pressure value, amplitude, and displacement in the vibration measuring device of 1st Example-3rd Example. It is a graph which shows the relationship between the pressure value, amplitude, and displacement in the vibration measuring device of 4th Example. (A) is a schematic diagram showing an example in which the variable damping device of the present invention is applied as a variable damping device for a base-isolated structure of a building, and (B) is applied as a variable damping device for a damping device installed in each layer of the building. (C) is a schematic diagram showing an example applied as a variable damping device of a mass damper device installed on the roof of a building.

<First embodiment>
A variable damping device 10 as an example of a fluid cylinder device according to a first embodiment to which the present invention is applied will be described.

  The variable damping device 10 of the present embodiment shown in FIG. 1 has a structure in which the resistance value of a piston cylinder type oil damper 40 described later can be changed in multiple stages or continuously. The variable damping device 10 is used for a damping device (damper) having a seismic isolation structure, a damping device (damper) installed in each layer of a building, a TMD damping device (damper), an AMD actuator, an actuator for an active seismic isolation device, and the like. It is done.

FIG. 12A shows an example in which the variable damping device 10 is applied to a seismic isolation structure 83 in which a building 80 is seismically isolated with a laminated rubber 82.
FIG. 12B shows an example in which the variable damping device 10 is applied to a vibration control device 84 installed in each layer of a building 80.
FIG. 12C shows an example in which the variable damping device 10 is applied to a mass damper device 87 in which an additional weight 86 is installed on the roof of a building 80 so as to be horizontally movable.

  In addition, although the variable damping device 10 of this embodiment is a structure which can change the resistance value of the oil damper 40 mentioned later in multiple steps or continuously, it is not limited to this. The resistance value may be two stages. Also, a fluid cylinder device that controls locking and unlocking may be used.

  Specifically, the oil damper 40 is locked against a small external force such as wind to suppress displacement, and the lock is released and the oil damper 40 is operated against a large external force such as an earthquake. Also good. Alternatively, it can be used as an oil damper 40 that gives optimum damping as a seismic isolation structure for normal earthquake shaking, and the seismic isolation layer displacement as a rock or high damping oil damper 40 for large earthquakes beyond expectations. Suppression may be performed.

  As shown in FIG. 1, the variable damping device 10 according to the first embodiment includes a piston cylinder type oil damper 40, a vibration measuring device 100, a resistance valve 20, and a pressure circuit 30. .

  The oil damper 40 has a structure in which a piston 44 moves in the axial direction in a cylinder 42 in which oil E is sealed. A first oil chamber 42A and a second oil chamber 42B having the same inner diameter before and after the piston 44 of the cylinder 42 are connected by a communication pipe 48. A resistance valve 20 is provided in the communication pipe 48, and the resistance value of the oil damper 40 is appropriately changed in multiple steps or continuously according to the throttle amount (opening degree) of the resistance valve 20.

  Specifically, the resistance valve 20 provides resistance to the movement of the oil E between the first oil chamber 42A and the second oil chamber 42B accompanying the movement of the piston 44 in the axial direction, and a damping force is generated by the fluid resistance. (Resistance value) is exhibited. Note that the throttle amount of the resistance valve 20 is controlled by the pressure output from the first output port 120A and the second output port 120B of the vibration measuring instrument 100 described later.

  As will be described later, there are two output ports of the vibration measuring instrument 100 of the present embodiment, the first output port 120A and the second output port 120B, and only the higher pressure is transmitted to the resistance valve 20 by the pressure circuit 30. It is configured as follows.

  The pressure circuit 30 may have any circuit configuration, but an example is shown in FIG. As shown in FIG. 2, the pressure circuit 30 has a circuit configuration having a valve 32A connected to the first output port 120A, a valve 32B connected to the second output port 120B, and a tank 34. Accordingly, the higher pressure valve 32A or the valve 32B of the first output port 120A and the second output port 120B is opened, and only the higher pressure is transmitted to the resistance valve 20.

  As shown in FIG. 3, the vibration measuring device 100 is provided between a rod side mounting portion 47 provided on the rod 46 of the oil damper 40 and a cylinder side mounting portion 49 provided on the end 42T of the cylinder 42. It is arranged and fixed to the rod side mounting portion 47 and the cylinder side mounting portion 49.

  The vibration measuring device 100 divides the inside of the cylindrical portion 110 into the first chamber 112A and the second chamber 112B in the axial direction and moves (displaces) in the axial direction. And a partition wall (piston) 114. A rod 116 extending in the axial direction is formed on the partition wall 114, and both ends of the cylindrical portion 110 in the axial direction, that is, the end portion 110A on the first chamber 112A side and the end portion 110B on the second chamber 112B side, respectively. It protrudes.

  A rod 116A protruding from the end portion 110A on the first chamber 112A side is attached to the rod side attachment portion 47, and an end portion 110B of the second chamber 112B is attached to the cylinder side attachment portion 49. Therefore, when the piston 44 (see FIG. 1) of the oil damper 40 moves, the partition wall 114 of the vibration measuring device 100 also moves (displaces) in the same manner.

  Although not shown in FIG. 3, a flow path is formed between the first chamber 112A and the second chamber 112B of the vibration measuring instrument 100, and when the partition wall 114 moves (displaces) in the axial direction, The oil R is configured to move between the first chamber 112A and the second chamber 112B.

  A first output port 120A is provided at the end 110A on the first chamber 112A side of the cylindrical portion 110 of the vibration measuring instrument 100, and a second output port 120B is provided at the end 110B on the second chamber 112B side. . The pressure of the oil R is output from the first output port 120A and the second output port 120B as the partition wall 114 is displaced in the axial direction. As described above, the throttle amount of the resistance valve 20 (see FIG. 1) is changed according to the pressure of the oil R.

The pressure of the oil R output from the first output port 120A and the second output port 120B is:
The axial displacement of the partition wall 114 is X,
The moving speed of the partition wall 114 in the axial direction is V,
The primary natural frequency of the installed building 80 (see FIG. 1) is the circular frequency ω.
Then,
f = √ {X ² + (V / ω) ² }
It is comprised so that it may be proportional to.
The value of this function f (output pressure) is defined as “the amount of state of the oil damper 40”.
Here, the displacement X and the velocity V are values for the partition wall 114 of the vibration measuring device 100, and are not values for the oil damper 40. However, since the partition wall 114 of the vibration measuring device 100 is provided so as to be displaced in proportion to the movement of the piston 44 of the oil damper 40, a value based on the displacement X and the velocity V of the partition wall 14 is set to “the value of the oil damper 40. It can be regarded as a “state quantity”.
A structure that outputs a pressure proportional to f = √ {X ² + (V / ω) ² } will be described later.

(Function and effect)
Next, the operation and effect of this embodiment will be described.

  The variable attenuator 10 used as shown in FIG. 1 may be desired to change its characteristics appropriately according to various states. For example, the damping force of the oil damper 40 is increased so that deformation does not increase during a large earthquake. In such a case, what is used as an index is the acceleration, speed, displacement of the building 80, stroke displacement of the oil damper 40, acceleration of the additional weight 86 of TMD or AMD, and the like.

When the characteristics of the oil damper 40 of the variable damping device 10 are switched according to the magnitude of the response in this way, f = √ {X ² + (V / ω) representing “the amount of state of the oil damper 40”. ² } is used as an index, and it is known that stable and effective control is possible (see Japanese Patent No. 4621364).

  That is, the variable damping device 10 of the present invention exhibits the effect of suppressing the acceleration to the maximum by an appropriate damping action at a small amplitude by appropriately switching the resistance value (damping force) in multiple stages or continuously. Although the acceleration increases at the amplitude, by suppressing the amount of displacement of the oil damper 40 to the maximum extent, damage to the building 80 (see FIG. 12) provided with the variable damping device 10 or various devices, and further destruction of the variable damping device 10 Can be prevented.

From another point of view, f = √ {X ² + (V / ω) ² } representing “the amount of state of the oil damper 40” is a value having a dimension of displacement, and the building 80 is stationary at the natural frequency ω. When oscillating, the value is almost constant. Therefore, if the resistance value (damping force) of the oil damper 40 is controlled based on the “state quantity of the oil damper 40”, stable control is performed in a steady state. Generation of shocking damper force (resistance force) due to breaking is prevented.

Here, in the variable damping device 10 of the present embodiment, f = √ {X where the pressure output from the first output port 120A and the second output port 120B of the vibration measuring device 100 represents “the state quantity of the oil damper 40”. ² + (V / ω) ² }. The throttle amount of the resistance valve 20 is directly controlled by this pressure. Therefore, the calculation by the calculation device (computer) for obtaining the index (f = √ {X ² + (V / ω) ² }) representing “the amount of state of the oil damper 40” becomes unnecessary.

  Therefore, the reliability is improved from the viewpoints of application to a building 80 that requires operation for a long period of time, dealing with loss of power, durability, and the like.

<Second embodiment>
A variable damping device 11 as an example of a fluid cylinder device according to a second embodiment to which the present invention is applied will be described. The same members as those in the first embodiment are denoted by the same reference numerals, and redundant description is omitted.

  As shown in FIG. 4, the variable damping device 11 of the second embodiment includes a solenoid valve 21, a signal conversion unit 38, and an arithmetic device (computer) 36. The electromagnetic valve 21 is controlled according to a control signal generated by the arithmetic device 36. The signal conversion unit 38 includes a pressure gauge, an amplifier, and the like, converts the pressure (the amount of state of the oil damper 40) output from the vibration measuring instrument 100 (pressure circuit 30) into an electric signal, and inputs the electric signal to the arithmetic device 36. . The arithmetic device 36 outputs a control signal for controlling the throttle amount of the electromagnetic valve 21 based on the electric signal (the state amount of the oil damper 40) output by the signal conversion unit 38.

(Function and effect)
Next, the operation and effect of this embodiment will be described.

Unlike the first embodiment, the variable attenuation device 11 of the present embodiment is provided with an arithmetic device (computer) 36. However, the calculation device 36 does not require calculation to obtain f = √ {X ² + (V / ω) ² } representing “the amount of state of the oil damper 40”. Therefore, the calculation in the calculation device 36 can be reduced, and the reliability is improved.

<Modifications of First Embodiment and Second Embodiment>
In the above embodiment, only the higher pressure of the pressure output from the first output port 120A and the second output port 120B of the vibration measuring instrument 100 is input to the resistance valve 20 transmission or signal conversion unit 38 by the pressure circuit 30. Is configured to do.

  However, the first output port 120A and the second output port 120B may be connected to separate resistance valves for control, or both are input to the signal conversion unit 38, and the signal conversion unit 38 only applies the higher pressure. You may make it convert into a signal.

  Further, the structure type of the oil damper 40 and the means for variable control of the resistance value are not limited to the above. For example, even with a piston cylinder type oil damper, for example, a plurality of oil paths having different resistance values are prepared in advance, and the resistance value through which the oil flows is changed by switching the path through which the oil flows by a resistance valve or a solenoid valve. It may be a system or the like. Alternatively, in the case of a damper using a magnetic fluid, the resistance value may be made variable by controlling the strength of the magnetic force applied to the passage through which the magnetic fluid flows.

<Details of vibration measuring instrument 100>
Next, details of the vibration measuring instrument 100 used in the variable damping device 10 of the first embodiment and the variable damping device 11 of the second embodiment will be described.

Here, the control based on the value of √ {X ² + (V / ω) ² } (the amount of state of the oil damper 40) and the control based on the value of {X ² + (V / ω) ² } Since they are essentially the same, the latter will be described here for the sake of clarity.

As shown in FIG. 5, the partition wall 114 is formed with an orifice 150 that communicates the first chamber 112A and the second chamber 112B. When the partition wall 114 moves (displaces) in the axial direction at a relative speed V, the pressure σ generated in the first chamber 112A or the second chamber 112B on the compression side is proportional to the square of V.
That means
σ = αV ²
It can be expressed as
Where α is a constant determined by the orifice 150. This α is set such that σ is proportional or substantially proportional to {X ² + (V / ω) ² } by the displacement X.

Considering the case of vibration at an amplitude (rated displacement) X0 and a circular frequency ω, using time t,
X = X0sin (ωt)
V = ωX0cos (ωt)
It can be.
Substituting these into {X ² + (V / ω) ² } described above,
{X ² + (V / ω) ² } = X0 ²
It becomes a constant value regardless of time.

on the other hand,

It becomes. This is a constant which is determined by the orifice 150,

If it is changed according to the displacement (stroke) X so as to be proportional to
{X ² + (V / ω) ² }
It is shown that a pressure proportional to is generated.

The constant α is generally α = β / A ^{2 with} respect to the opening area A of the orifice 150.
(Β is a constant). The above formula is only an example.

And from the above formula,

It becomes.
That is, the effective opening area A of the orifice 150 at the displacement (stroke) X is expressed by K = √ {X0 ² −X ² }
It can be seen that it may be proportional to

  However, in practice, it is difficult or difficult to change the effective opening area A of the orifice 150 of the partition wall 114 in accordance with the axial displacement (movement) X of the partition wall 114.

Therefore, a specific structure for making the effective opening area of the orifice 150 at the displacement X proportional to √ {X0 ² −X ² } will be described as an example.

[Example]
In the vibration measuring devices 101, 102, 103, and 104 of the first to fourth embodiments described below, the same members as those of the above-described vibration measuring device 100 are denoted by the same reference numerals, and redundant descriptions are omitted. To do.

(First Example)
First, the first embodiment will be described.

  As shown in FIG. 6, in the vibration measuring instrument 101 of the first embodiment, a groove (orifice) 160 is formed in the peripheral wall 110 </ b> C of the cylindrical portion 110. Although the axial depth of the groove 160 is constant (FIGS. 6A, 6C, 6D, and 6E), the shape viewed from the direction orthogonal to the axial direction is an elliptical shape. (FIG. 6B). That is, the gap S1 between the partition wall 114 and the peripheral wall 110C of the cylindrical portion 110 has the widest center position in the axial direction and narrows outward in the axial direction (FIGS. 6B, 6D, and 6E). )).

The gap S1 corresponds to the orifice 150 in FIG. 5, and the oil R moves between the first chamber 112A and the second chamber 112B through the gap S1. The flow path area (FIGS. 6D and 6E) on the inflow side (the portion corresponding to the end of the partition wall 114 in the traveling direction) of the gap S1 is proportional to √ {X0 ² −X ² }. Is configured to do. In this embodiment, since the depth of the groove 160 is constant in the axial direction, the width of the groove 160 is configured to be proportional to √ {X0 ² −X ² }.

(Second embodiment)
Next, a second embodiment will be described.

  As shown in FIG. 7, in the vibration measuring instrument 102 of the second embodiment, a groove (orifice) 162 is formed in the peripheral wall 110 </ b> C of the cylindrical portion 110. The shape of the groove 160 viewed from the direction orthogonal to the axial direction is a band shape and is constant in the axial direction (FIG. 7B), but the axial depth is shallower toward the outer side in the axial direction (FIG. 7 ( A), (C), (D), (E))). That is, the gap S2 between the partition wall 114 and the peripheral wall 110C of the cylindrical portion 110 is deepest in the axial center position and shallows outward in the axial direction (FIGS. 7A, 7C, 7D, 7E). )).

The gap S2 corresponds to the orifice 150 in FIG. 5, and the oil R moves between the first chamber 112A and the second chamber 112B through the gap S2. The flow path area (FIGS. 7D and 7E) on the inflow side (the portion corresponding to the end of the partition wall 114 in the traveling direction) of the gap S2 is proportional to √ {X0 ² −X ² }. Is configured to do. In this embodiment, since the width of the groove 162 is constant in the axial direction, the depth of the groove 162 is configured to be proportional to √ {X0 ² −X ² }.

(Third embodiment)
Next, a third embodiment will be described.

  As shown in FIG. 8, in the vibration measuring instrument 103 of the third embodiment, the cylindrical portion 111 has a double structure including an inner peripheral wall portion 113 and an outer peripheral wall portion 115. The inside of the inner peripheral wall 113 is a first chamber 112A and a second chamber 112B, and a tank 117 is provided between the inner peripheral wall 113 and the outer peripheral wall 115.

  Check valves 166A and 166B are provided at both axially outer ends of the inner peripheral wall 113 (the first chamber 112A and the second chamber 112B) of the cylindrical portion 111. The check valves 166A and 166B are configured so that the oil R can move from the tank 117 side to the inner peripheral wall 113 (the first chamber 112A and the second chamber 112B) side, but not vice versa. . Further, slit-like orifices 164A and 164B are formed in the inner peripheral wall portion 113.

As shown in FIG. 8B, the orifices 164A and 164B are widened outward in the axial direction. The opening areas S3A and S3B of the orifices 164A and 164B are formed to be proportional to √ {X0 ² −X ² }.

(Fourth embodiment)
Next, a fourth embodiment will be described.

  In the vibration measuring instrument 104 of the fourth embodiment shown in FIG. 9, the cylindrical portion 111 has a double structure composed of an inner peripheral wall portion 113 and an outer peripheral wall portion 115. The inside of the inner peripheral wall 113 is a first chamber 112A and a second chamber 112B, and a tank 117 is provided between the inner peripheral wall 113 and the outer peripheral wall 115.

  Check valves 166A and 166B are provided at both axially outer ends of the inner peripheral wall 113 (the first chamber 112A and the second chamber 112B) of the cylindrical portion 111. The check valves 166A and 166B are configured so that the oil R can move from the tank 117 side to the inner peripheral wall 113 (the first chamber 112A and the second chamber 112B) side, but not vice versa. . Orifices 168A, 168B are discretely formed in the inner peripheral wall portion 113 in the axial direction.

As shown in FIG. 9B, the orifices 168A and 168B increase in density (number per unit length in the axial direction) toward the outside in the axial direction. The density (number per unit length in the axial direction) of the orifices 168A and 168B is formed to be proportional to √ {X0 ² −X ² }.

[Pressure values of the first to fourth embodiments]
Next, pressure values output from the first output port 120A and the second output port 120B of the vibration measuring devices 101, 102, 103, and 104 of the first to fourth embodiments will be described.

The vibration measuring instruments 101, 102, 103, and 104 of the first to fourth embodiments have the first output port 120A and the second output port 120B that are on the compression side due to the movement (displacement) of the partition wall 114 in the axial direction. A pressure proportional to {X0 ² −X ² } is generated. This pressure has a constant value regardless of the displacement X when vibrating with a sinusoidal wave having an amplitude (rated displacement) X0 and a circular frequency ω.

  The pressure values output from the first output port 120A and the second output port 120B are continuous orifices (including grooves) as in the vibration measuring instruments 101, 102, 103 of the first to third embodiments. When changing, the amplitude X1 of the displacement X is the same as the rated displacement X0 and becomes constant when vibrating at the circular frequency ω. However, when the amplitude X1 is different from the rated displacement X0, it is not constant.

FIG. 10 shows this. The vertical axis represents the pressure value, and the horizontal axis represents the displacement X of the partition wall 114 normalized by the rated displacement X0. The theoretical value √ {X ² + (V / ω) ² } is a thin broken line, and the pressure values output from the vibration measuring instruments 101, 102, 103 of the first to third embodiments are bold lines. The broken line (X1 = 1.2X0), the solid line (X1 = 1.0X0), the alternate long and short dash line (X1 = 0.8X0), and the two-dot broken line (X1 = 0.6X0).

From this graph, when the vibration vibrates with the amplitude X1 = the rated displacement X0, the pressure values output from the vibration measuring devices 101, 102, 103 coincide with the value of √ {X ² + (V / ω) ² }. However, when the amplitude X1 is smaller than the rated displacement X0, the pressure value is less than the value of √ {X ² + (V / ω) ² }, and when the vibration amplitude X1 is larger than the rated displacement X0, the pressure value is √. It exceeds the value of {X ² + (V / ω) ² }. Further, when the displacement X of the partition wall 114 is small, the difference between the two is small, and when the displacement X is large, the difference between the two is large.

  FIG. 11 shows the case of the vibration measuring instrument 104 of the fourth embodiment. In this example, ten orifices 168A and 168B are dispersedly arranged.

The orifices 168A and 168B are zigzag because they are discretized, but when the amplitude X1 is smaller than the rated displacement X0 as in FIG. 9, the pressure value is √ {X ² + (V / ω) ² } When the vibration amplitude X1 is larger than the rated displacement X0, the pressure value exceeds the value of √ {X ² + (V / ω) ² }. Further, when the displacement X is small, the difference between the two is small, and when the displacement X is large, the difference between the two is large. In addition, even when vibrating with the amplitude X1 = the rated displacement X0, it is zigzag, and the zigzag increases as the displacement X approaches the rated displacement X0.

Thus, except for the amplitude X1 = the rated displacement X0, there is a difference between the pressure value output from the first output port 120A and the second output port 120B and the theoretical value √ {X ² + (V / ω) ² }. . However, the pressure values output from the first output port 120A and the second output port 120B can be used as an approximate reference (state quantity of the oil damper 40).

  Further, for example, when the characteristics of the damping device such as the oil damper 40 are switched depending on whether the vibration is larger or smaller than the amplitude X1 = the rated displacement X0, it is only necessary to generate a pressure as a reference for the switching. Even if there is a difference between the values, no problem occurs, or even if a problem occurs, the effect is small.

  As shown in FIGS. 10 and 11, when the displacement X approaches the rated displacement X0 with respect to the vibration having the amplitude X1 larger than the rated displacement X0, the pressure rapidly increases. Furthermore, when the displacement X exceeds the rated displacement X0, the orifice disappears. Therefore, a relief circuit may be provided so that the pressure does not exceed a predetermined threshold value.

In the above embodiment, the areas of the grooves 160 and 162, the areas of the orifices 164A and 164B, and the density (number per unit length in the axial direction) of the orifices 168A and 168B are √ {X0 ² −X ² }. Although it is proportional, in actuality, it varies depending on the shape and length of the flow path that communicates between the first chamber 112A and the second chamber 112B, such as a groove and an orifice. Therefore, it is necessary to appropriately adjust the area and density.

In short, α, which is a constant determined by the flow path connecting the first chamber 112A and the second chamber 112B, such as a groove or an orifice, is set.

Any structure that changes in accordance with the displacement X to be proportional to

  In the vibration measuring devices 101, 102, 103, and 104 of the above-described embodiments, all are rod-types having rods 116A and 116B on both sides of the partition wall (piston) 114, but the present invention is not limited to this. A single rod type having a rod only on one side of the partition wall (piston) 114 may be used. However, in the case of the single rod type, the pressure receiving area of the partition wall 114 is different depending on the presence or absence of the rod in the first chamber 112A and the second chamber 112B, so the flow rates flowing by pushing and pulling are different. For this reason, it is desirable to provide a sub-tank for adjusting the flow rate (holding the difference).

<Others>
In addition, this invention is not limited to the said embodiment and Example.

In the above embodiment and examples, the pressure value output from the first output port 120A and the second output port 120B is a theoretical value of √ {X ² + (V / ω) ² } (state quantity of the oil damper 40). It is comprised so that it may be proportional to. However, as in the first to fourth embodiments, the pressure value and the theoretical value may not match. It is only necessary to approximate {X ² + (V / ω) ² } (state quantity of the oil damper 40). Alternatively, it may be configured to be proportional to a function other than √ {X ² + (V / ω) ² } (the amount of state of the oil damper 40). For example, the square part of the above equation may be 1.8 or 2.2.

  Moreover, in the said embodiment and Example, although the vibration measuring device was filled with oil, it is not limited to this. It may be a liquid other than oil or a gas.

  Needless to say, various embodiments can be implemented without departing from the scope of the present invention.

10 Variable damping device (example of fluid cylinder device)
11 Variable damping device (example of fluid cylinder device)
20 Resistance valve (resistance change means)
21 Solenoid valve (resistance change means)
40 Oil damper (example of fluid cylinder body)
DESCRIPTION OF SYMBOLS 100 Vibration measuring device 101 Vibration measuring device 102 Vibration measuring device 103 Vibration measuring device 104 Vibration measuring device 110 Cylinder part 112A 1st chamber 112B 2nd chamber 114 Bulkhead 120A 1st output port (output part)
120B Second output port (output unit)
160 groove (orifice)
162 Groove (orifice)
164A orifice 164B orifice 168A orifice 168B orifice

Claims (3)

A cylinder part filled with fluid;
A partition wall that axially divides the inside of the cylindrical portion into a first chamber and a second chamber, and that is displaced in the axial direction;
The flow path area on the inflow side of the fluid that is provided in the cylindrical portion and flows through the first chamber and the second chamber changes so as to be proportional to the function value using the displacement of the partition wall and the rated displacement. An orifice to be
An output unit for outputting the pressure of the fluid in the first chamber and the second chamber,
A vibration measuring instrument comprising: The function is K,
The displacement of the partition wall is X,
The rated displacement of the partition wall is X0,
Then,
K = √ {X0 ² −X ² }
Is,
The vibration measuring instrument according to claim 1. A fluid cylinder body in which a piston moves in an axial direction in a cylinder filled with fluid;
The vibration measuring instrument according to claim 1 or 2, wherein the partition wall is provided so as to be displaced in proportion to the movement of the piston of the fluid cylinder body.
Resistance changing means for changing the resistance specification of the fluid cylinder body by the pressure output from the output unit of the vibration measuring device;
A fluid cylinder device comprising: