JP6000872B2 - Control method of hydraulic damper open / close control valve and hydraulic damper used in the method - Google Patents

Description

  The present invention relates to a control method of a hydraulic damper on / off control valve for controlling an on / off control valve provided in a hydraulic damper for vibration control used to reduce shaking of a building due to vibration external force such as earthquake and wind, and to the method The present invention relates to a hydraulic damper used.

  As a hydraulic damper type damping device for reducing the shaking of a building, there is a variable damping device capable of controlling the opening / closing control valve in two stages of fully open and fully closed (see Patent Documents 1 and 2).

  As shown in FIG. 15, this type of hydraulic damper is provided in a cylinder, a double rod type piston that reciprocates in the cylinder, a hydraulic chamber provided on both sides of the piston, and a flow path that connects the two hydraulic chambers. It has a feature that the damping coefficient of the hydraulic damper can be switched between two levels of a maximum value Cmax and a minimum value Cmin by using an open / close control valve or the like as a basic structure and switching the opening degree of the open / close control valve. As a method for opening and closing the open / close control valve, a method of performing current control from a controller using an electromagnetic valve (see, for example, Patent Document 1), or a hydraulic pressure that is automatically controlled to open / close using hydraulic pressure fluctuation (generation of a pressure difference). There is a method using a circuit (for example, see Patent Document 2).

  Since such a hydraulic damper is attached between building layers via a brace as shown in FIG. 16- (a), the mechanical characteristics of the device unit including the brace and the damper are as shown in FIG. 16- (b). , A spring having rigidity K and a dashpot having a damping coefficient C are represented by a Maxwell model connected in series.

  FIGS. 17A to 17C schematically show the movement of the hydraulic damper controlled by the conventional switching law. While the building is oscillating from the maximum amplitude (Fig. 17 (a)) to the maximum amplitude on the opposite side (Fig. 17 (b)), the open / close control valve is closed and the brace is rigidly attached to the damper. Finally, once the valve is opened at the maximum point of deformation amplitude (FIG. 17- (b)) and the strain energy stored in the brace is unloaded and absorbed as C = Cmin, the valve is closed again and C = Cmax. (FIG. 17- (c)). Thus, the relationship between the damper load and the interlayer deformation formed by switching the valve opening degree of the open / close control valve at the maximum point of vibration amplitude is as shown in FIG.

  In FIG. 18, the loop area related to load deformation represents the amount of vibration energy absorbed by the damper, which absorbs a larger amount of energy than a general hydraulic damper with a constant C, and greatly reduces the vibration of the structure. I can see that

  FIG. 19 shows the relationship between the damper load and the deformation of only the dashpot (the damper deformation excluding the brace deformation from the interlayer deformation). In a general hydraulic damper with a constant C, the deformation of the dashpot is limited to a value smaller than the amplitude δ of the interlayer deformation. On the other hand, switching control is performed so that C = Cmin by opening the valve once at the maximum amplitude point of vibration. By doing so, the dashpot undergoes the same δ deformation as the interlayer deformation. The switching control has the effect of expanding the deformation of the dashpot (hydraulic damper), which is the reason why the energy absorption efficiency is improved.

Japanese Patent No. 2995954 (paragraphs 0024 to 0039, FIGS. 1 to 4) Japanese Patent No. 4042366 (Claim 1, Claim 2, Paragraphs 0025 to 0069, FIGS. 1 to 4)

  The load deformation relationship shown in FIG. 18 is the theoretically maximum loop that can be realized by switching the damping coefficient C of the Maxwell model shown in FIG. Therefore, it has been considered that there is only an active method of applying a control force by supplying energy from the outside, such as driving a motor with electric power, to exceed this.

  The present invention proposes a control method for an open / close control valve that exhibits an energy absorption capacity exceeding the loop area shown in FIG. 18 while using a hydraulic damper having only passive resistance elements.

According to a first aspect of the present invention, there is provided a control method for a hydraulic damper on / off control valve comprising a cylinder, a piston that reciprocates in the cylinder, hydraulic chambers provided on both sides of the piston, and a flow connecting the hydraulic chambers. A hydraulic damper having an open / close control valve connected to a road and capable of switching between an open state and a closed state , wherein the hydraulic damper is connected to the cylinder and can store pressure oil, and the auxiliary hydraulic tank, An open / close control valve connected between each hydraulic chamber and capable of switching between an open state and a closed state ,
While the piston is moving in either direction, the full open / close control valve is closed to generate pressure in the hydraulic chamber on one side, and when the direction of movement of the piston is reversed, it becomes the high pressure side. Opening one of the open / close control valves connecting the one hydraulic chamber and the auxiliary hydraulic tank to move the pressure oil in the one hydraulic chamber to the auxiliary hydraulic tank;
Thereafter, the open / close control valve is closed, and the open / close control valve connecting the both hydraulic chambers is opened to release the pressure in the hydraulic chamber on the high pressure side. After the difference is eliminated, the open / close control valve that is open is closed, and any open / close control valve that connects the other hydraulic chamber on the opposite side of the one side to the auxiliary hydraulic tank is opened. It is a constituent requirement that the pressure oil in the auxiliary hydraulic tank is moved to the other hydraulic chamber and a series of operations for closing the open / close control valve is performed.

  As shown in FIG. 1- (a), the hydraulic damper has a structure common to the hydraulic damper of Patent Document 2 described above, and a flow path connected in parallel between hydraulic chambers A and B partitioned on both sides of the piston 3. An opening / closing control valve C that connects both hydraulic chambers A and B is connected to a part of 4. When the open / close control valve C is controlled (held) in a closed state, a hydraulic damper is used to connect a connecting material (hereinafter referred to as a brace 21) such as a brace 21 in the frame 20, such as a brace 21 or the like, which is connected to the piston rod 3A. 1 is fixed. The flow path 4 connecting the hydraulic chambers A and B is branched, and the auxiliary hydraulic tank 7 is connected to the branched flow paths 5 and 6, and the flow path 5 connecting the auxiliary hydraulic tank 7 and the hydraulic chambers A and B, Open / close control valves D and E are connected to a part of 6.

  Of the open / close control valves D and E that connect the auxiliary hydraulic tank 7 and the respective hydraulic chambers A and B, one of the open / close control valves D (E) is one of the hydraulic chambers A and B or the piston 3. After one of the hydraulic chambers A (B) becomes relatively high pressure due to the movement toward the hydraulic chamber A (B) side, the piston 3 is opened when the direction of movement of the piston 3 is reversed. The pressure oil from the hydraulic chamber A (B) is moved to the auxiliary hydraulic tank 7. The other open / close control valve E (D) once opens the open / close control valve C connecting the hydraulic chambers A and B after the pressure oil from the high pressure side hydraulic chamber A (B) moves to the auxiliary hydraulic tank 7. Then, after the pressures of the hydraulic chambers A and B are balanced, the hydraulic control chamber C is opened when the open / close control valve C is closed, and the pressure oil from the auxiliary hydraulic tank 7 is moved to the other hydraulic chamber B (A).

  There is no distinction between the hydraulic chamber A and the hydraulic chamber B, and there is no distinction between the open / close control valves D and E. In FIG. 1- (a), when the hydraulic chamber A first becomes the high pressure side, the pressure oil from the hydraulic chamber A is assisted through the open / close control valve D that connects the hydraulic chamber A and the auxiliary hydraulic tank 7. It flows to the hydraulic tank 7. After equilibration of the pressures of both hydraulic chambers A and B due to opening of the open / close control valve C, the pressure oil from the auxiliary hydraulic tank 7 flows into the hydraulic chamber B via the open / close control valve E connecting the hydraulic chamber B and the auxiliary hydraulic tank 7. However, when the hydraulic chamber B first becomes the high pressure side, the pressure oil from the hydraulic chamber B flows to the auxiliary hydraulic tank 7 through the opening / closing control valve E. Thereafter, the pressure oil from the auxiliary hydraulic tank 7 flows into the hydraulic chamber A through the opening / closing control valve D.

  The operation of the hydraulic damper 1 will be described with reference to FIGS. 2A to 2E schematically showing the movement of the hydraulic damper 1 and the brace 21 employing the method of the present invention while the building is vibrating. While the frame 20 is deformed in one direction due to vibration (between FIGS. 2A to 2B), by holding (controlling) all the open / close control valves C, D, E in the closed state. The hydraulic damper 1 is in a state of being rigidly connected to the brace 21. In the first aspect, “while the piston is moving in any direction” means (continuously) as long as the frame 20 is deformed in one direction by vibration.

  When a load corresponding to the interlayer deformation is generated in the brace 21, pressure is generated in the hydraulic chamber A (B) on either side across the piston 3. First, at the maximum amplitude point of vibration of the frame 20, the open / close control valve D (E) that connects the hydraulic chamber A (B) where the pressure is generated and the auxiliary hydraulic tank 7 is opened, and the hydraulic oil in the hydraulic chamber A (B) is discharged. Move to auxiliary hydraulic tank 7. When the frame 20 reaches the maximum amplitude point of vibration, this corresponds to “when the direction of movement of the piston is reversed” in claim 1. When the pressure oil from the hydraulic chamber A (B) moves to the auxiliary hydraulic tank 7, the pressure in the hydraulic chamber A (B) decreases slightly, and the piston 3 that has been in the fixed state moves toward the hydraulic chamber A (B). The movement becomes possible, and the brace 21 is unloaded a little accordingly (FIG. 2- (c)).

  When the pressure in the hydraulic chamber A and the auxiliary hydraulic tank 7 becomes equal, when the opening / closing control valve D is closed and the opening / closing control valve C is opened, the load of the brace 21 is completely unloaded and the brace 21 is in the neutral position. Return to FIG. 2- (d). At this time, the pressure in the hydraulic chamber A (B) on the high pressure side is released (unloaded), and the pressure difference between the hydraulic chambers A and B is eliminated. When the opening / closing control valve C is closed and the opening / closing control valve E is opened after the unloading of the brace is completed, the pressure oil in the auxiliary hydraulic tank 7 flows into the hydraulic chamber B on the other side. At this time, since the pressure in the hydraulic chamber B becomes higher than the pressure in the hydraulic chamber A, the piston 3 is pushed toward the hydraulic chamber A in the cylinder 2, and a force is applied to the brace 21, and FIG. The brace 21 is deformed in the opposite direction (FIG. 2- (e)). When the pressure in the auxiliary hydraulic tank 7 and the pressure in the hydraulic chamber B become equal, the open / close control valve E is closed.

  Since the time required for the series of opening / closing operations from FIG. 2B to FIG. 2E is sufficiently short compared to the building vibration cycle, the external force is applied in a state where an offset deformation (load) is applied to the brace 21. With the change of direction, the reverse vibration starts.

  FIG. 3 is a view showing the relationship between the damper load and the interlayer deformation according to the method of the present invention in comparison with a conventional switching control and a general hydraulic damper, and points a to e in FIG. ) To (e). FIG. 4 shows the relationship between the damper load and the deformation of only the hydraulic damper (deformation excluding brace deformation from interlayer deformation). It can be seen that the deformation of the damper portion can be expanded to more than the interlayer deformation δ by temporarily moving the pressure to the auxiliary hydraulic tank and using it to apply offset deformation to the brace.

  By the way, when the open / close control valve E is closed after the completion of FIG. It can contribute to the improvement of energy absorption efficiency with repetition of vibration. FIG. 5 shows a load-deformation locus when vibration is started from a stationary state. As the vibration is repeated, the pressure in the auxiliary hydraulic tank 7 is accumulated, so that the energy absorption efficiency is increased and reaches a steady state several times. Reference numerals (numerals) in FIG. 5 indicate the path of load deformation accompanying the repeated interlayer deformation from the state before the frame 20 is deformed. Thus, although the residual pressure of the auxiliary hydraulic tank 7 acts in a good direction, the vibration cycle of the building is slower than the series of opening and closing operations shown in FIGS. 2- (a) to (e). In addition, the pressure in the auxiliary hydraulic tank 7 may be released.

  FIG. 6 shows a load deformation relationship when it is assumed that the residual pressure in the auxiliary hydraulic tank 7 is completely released after FIG. Compared with FIG. 5, although the loop area is slightly smaller, the energy absorption is still greater than that of the conventional switching control.

FIG. 7 shows the influence of the equivalent stiffness k of the auxiliary hydraulic tank on the stiffness K of the Maxwell model shown in FIG. The optimum stiffness setting value and efficiency change depending on whether the pressure of the auxiliary hydraulic tank is maintained during vibration (in the case of FIG. 5) or is released (in the case of FIG. 6), but k / K is approximately 0. If it can be set to about .5 to 3.0, the efficiency of about 1.5 times or more of the conventional switching control is realized. If the value of k deviates significantly from the above range, the efficiency is lowered, but the efficiency is not lowered as compared with conventional switching control. As a method of storing pressure in the auxiliary hydraulic tank, when using the compression rigidity of the working fluid, if the auxiliary hydraulic tank capacity is V, the volumetric elastic modulus of the working fluid is G, and the piston area of the damper is A The equivalent rigidity k of the hydraulic tank is expressed as k = GA ² / V.

On the other hand, if an auxiliary hydraulic tank using a spring or the like is used, the rigidity adjustment is further facilitated. Since the compression rigidity of the working fluid (oil) is high, if the capacity of the auxiliary hydraulic tank is small, k / K is larger than about 3.0, and therefore a sufficiently large tank capacity is given to avoid it (k = It is necessary to increase the V of GA ² / V). However, if the system is a piston type accumulator, the spring stiffness can be directly adjusted.

  The hydraulic damper used in the method according to claim 1 includes an electric drive means for operating opening / closing control valves C, D, E by supplying an external current (Claim 2), and both hydraulic pressures. There are cases where hydraulic drive means for operating opening / closing control valves C, D, E based on fluctuations in the pressure difference between the chambers A, B is provided (Claim 3), and electrical drive means and hydraulic drive means are provided. (Claim 4). The electric drive means is a method mainly using an electromagnetic valve, and the hydraulic drive means is a method using a switching valve driven mainly by hydraulic pressure.

  When the frame 20 is most deformed in either direction, the open / close control valve C is immediately opened while the hydraulic chambers A and B are connected to freely move the hydraulic oil between the hydraulic chambers A and B. The hydraulic oil in the hydraulic chamber A (B) that has reached the high pressure side is allowed to flow into the auxiliary hydraulic tank to maintain the hydraulic energy, and the open / close control valve C is opened, so that the hydraulic chamber A Since the hydraulic energy in the auxiliary hydraulic tank is injected into the opposite hydraulic chamber B (A) after the pressure between B and B is brought into an equilibrium state, the deformation of the brace 21 can be expanded more than the interlayer deformation of the frame 20. .

  As a result, the hysteresis loop representing the relationship between the load (hydraulic damper load) and the deformation (interlayer deformation) during the deformation of the frame 20 in one cycle can be drawn with a larger area than the conventional history loop. Energy absorption efficiency is improved.

(A) is sectional drawing which showed typically the structure of the hydraulic damper of this invention, (b) is sectional drawing which showed typically the hydraulic circuit diagram shown in FIG. 8 as an example of (a). (A) is an elevation view showing a state in which the frame incorporating the hydraulic damper shown in FIG. 1 is deformed in either direction, and (b) is the largest interlayer deformation from the state of (a). (C) is an elevation view showing the state when the open / close control valve D is opened immediately after the state of (b), and (d) is an elevation view of (c). FIG. 5E is an elevation view showing the state when the open / close control valve D is closed and the open / close control valve C is opened immediately after the state (the piston is free to move); FIG. It is the elevation which showed a mode when the on-off control valve C was closed and the on-off control valve E was made into the open state. FIG. 2 is a hysteresis characteristic diagram showing a load-deformation (interlayer deformation) relationship of a hydraulic damper during one cycle of vibration when the control shown in FIGS. 2- (a) to (e) is performed. FIG. 4 is a hysteresis characteristic diagram showing a load-deformation (interlayer deformation) relationship of a hydraulic damper when a frame deformation amount is subtracted from the interlayer deformation in FIG. 3. FIG. 6 is a hysteresis characteristic diagram showing a load-deformation (interlayer deformation) relationship when it is assumed that the pressure of the auxiliary hydraulic tank is maintained during half-cycle vibration. FIG. 6 is a hysteresis characteristic diagram showing a load-deformation (interlayer deformation) relationship when it is assumed that the pressure of the auxiliary hydraulic tank is not maintained during half-cycle vibration. The ratio k / K of the equivalent stiffness k of the auxiliary hydraulic tank to the stiffness K of the dynamic model shown in FIG. 2- (b) and the energy absorption amount of the hydraulic damper subjected to the conventional switching control of the energy absorption amount of one cycle. It is the graph which showed the relationship with the ratio with respect to. FIG. 3 is a hydraulic circuit diagram showing an example of connection between a hydraulic damper and each open / close control valve when opening / closing of each open / close control valve is controlled based on a command from a controller to a solenoid attached to each open / close control valve. FIG. 3 is a hydraulic circuit diagram showing an example of connection between a hydraulic damper and each open / close control valve when opening / closing of each open / close control valve is controlled due to a pressure difference between both hydraulic chambers of the hydraulic damper. FIG. 10 is a hydraulic circuit diagram showing an example of connection between the hydraulic damper and each open / close control valve when the controller shown in FIG. 9 and the solenoid that operates based on its command are added to the example shown in FIG. 9. (A) is a schematic diagram showing a state in which the relief valve 12 is incorporated at a position where the two hydraulic chambers of the hydraulic damper shown in FIG. 1- (a) are connected, and (b) is connected between the hydraulic chambers shown in (a). FIG. 6 is a hysteresis characteristic diagram showing a load-deformation (interlayer deformation) relationship of a hydraulic damper when a relief valve is activated. FIG. 9 is a hydraulic circuit diagram illustrating a connection example between a hydraulic damper and each open / close control valve when a relief valve is connected to a flow path between hydraulic chambers of the hydraulic damper in the example illustrated in FIG. 8. FIG. 9 is a hydraulic circuit diagram showing an example of connection between the hydraulic damper and each on-off control valve when relief valves are connected to the flow path between the hydraulic chambers of the hydraulic damper and the buffer and accumulator in the example shown in FIG. It is. FIG. 10 is a hydraulic circuit diagram showing an example of connection between the hydraulic damper and each open / close control valve when a relief valve is connected to the passage between the hydraulic chambers of the hydraulic damper in the example shown in FIG. 10 and two places between the buffer and the accumulator. It is. It is sectional drawing which showed typically the structure of the conventional damping coefficient switching type hydraulic damper which has an on-off control valve. 15A is an elevation view showing a state in which the hydraulic damper shown in FIG. 15 is installed across the frame between the seismic element such as a brace arranged in the column / beam frame, and FIG. It is the schematic diagram which showed the mechanical model of the apparatus part which match | combined the brace and hydraulic damper which are shown. FIG. 16A is an elevation view showing a state in which the frame shown in FIG. 16A causes the maximum interlayer deformation in either direction, and FIG. 16B shows the maximum interlayer deformation in the opposite direction. (C) is an elevational view showing a state when the opening / closing control valve is opened immediately after the state of (b) to freely move the piston in the cylinder. FIG. 18 is a hysteresis characteristic diagram showing a load-deformation (interlayer deformation) relationship of the hydraulic damper during vibration of one cycle shown in FIGS. 17 (a) to (c). FIG. 19 is a hysteresis characteristic diagram showing a load-deformation (damper deformation) relationship of the hydraulic damper when the amount of brace deformation is subtracted from the interlayer deformation in FIG. 18.

  Hereinafter, the best mode for carrying out the present invention will be described with reference to FIGS.

The hydraulic damper 1 is connected to a cylinder 2, a piston 3 that reciprocates in the cylinder 2, hydraulic chambers A and B provided on both sides of the piston 3, and a flow path 4 that connects both hydraulic chambers A and B, and is opened. An open / close control valve C that can be switched between a state and a closed state, an auxiliary hydraulic tank 7 that is connected to the cylinder 2 and can store pressure oil, and is connected between the auxiliary hydraulic tank 7 and each of the hydraulic chambers A and B, and is opened. Open / close control valves D and E that are switched between a state and a closed state are provided.

  FIG. 8 shows the hydraulic damper 1 shown in FIG. 1- (b) on the basis of a command from the controller 8 as an electric drive means for operating the opening / closing of all the opening / closing control valves C, D, E by supplying an external current. An example of connection between the hydraulic damper 1 and each of the on / off control valves C to E when controlling all the on / off control valves C to E is shown.

  In the example shown in FIG. 1- (a), since all the open / close control valves C to E have no directionality, when the hydraulic chamber A becomes the high pressure side, the pressure oil in the hydraulic chamber A is switched to the open / close control valve D. The pressure oil in the auxiliary hydraulic tank 7 moves to the opposite hydraulic chamber B through the open / close control valve E. When the hydraulic chamber B reaches the high pressure side, the pressure oil in the hydraulic chamber B moves to the auxiliary hydraulic tank 7 through the open / close control valve E, and the pressure oil in the auxiliary hydraulic tank 7 passes through the open / close control valve D to the opposite hydraulic pressure. Move to chamber A.

  FIG. 1- (b) schematically shows the structure of a hydraulic damper as another example of FIG. 1- (a) when the on-off control valves C to E in FIG. 1- (a) have directionality. FIG. 8 corresponds to a specific example of the hydraulic circuit diagram shown in FIG. In FIG. 1- (a), the pressure oil can move between the hydraulic chamber A and the auxiliary hydraulic tank 7 from the high pressure side to the low pressure side through the open / close control valve D, and the high pressure between the hydraulic chamber B and the auxiliary hydraulic tank 7 through the open / close control valve E. It can move from the side to the low pressure side. On the other hand, in (b), the pressure oil from one of the hydraulic chambers A (B) on the high pressure side can be moved to the auxiliary hydraulic tank 7 through the open / close control valve D by the switching valve 2A, and the pressure from the auxiliary hydraulic tank 7 is increased. Oil can move to one of the high pressure side hydraulic chambers B (A) through the open / close control valve E.

  1B, when the hydraulic chamber A is on the high pressure side due to the movement of the piston 3, the switching valve 2A connects the flow path between the high pressure side hydraulic chamber A and the open / close control valve D. When the opening / closing control valve D is opened when the direction of movement of the piston 3 is reversed, the pressure oil from the hydraulic chamber A moves to the auxiliary hydraulic tank 7 through the opening / closing control valve D. After the pressure in the auxiliary hydraulic tank 7 and the hydraulic chamber A reaches equilibrium, once the open / close control valve D is closed and then the open / close control valve C is opened, the pressure in the hydraulic chamber A flows into the hydraulic chamber B and is released. Is done. When the opening / closing control valve C is closed when the pressure difference between the hydraulic chambers A and B is eliminated, the piston 3 has already started to move slightly in the opposite direction. Since the hydraulic chamber B is slightly on the high pressure side, the switching valve 2A is switched, and the flow path of the hydraulic chamber B and the open / close control valve E is connected. Thereafter, when the opening / closing control valve E is opened, the pressure oil in the auxiliary hydraulic tank 7 moves to the hydraulic chamber B. In FIG. 1- (b), the switching valve 2A serves to connect the high-pressure side hydraulic chamber A (B) to the on-off control valve D and the on-off control valve E. It is not necessary when using a bidirectional valve as shown.

  In the example shown in FIG. 8, solenoid valves D1 and E1 for operating the opening / closing control valve D and the opening / closing control valve E are connected to the opening / closing control valve D and the opening / closing control valve E, respectively. A solenoid valve C1 that operates to open and close the control valve C is connected. In this example, when either of the hydraulic chambers A and B is in the high pressure side, the pressure from the high pressure side hydraulic chamber A (B) is A switching valve 2A for flowing oil to the opening / closing control valve D and the opening / closing control valve C side is connected.

  The switching valve 2A is connected to a flow path 4 that connects both hydraulic chambers A and B. In the switching valve 2A, when the pressure in one hydraulic chamber A (B) exceeds the pressure in the other hydraulic chamber B (A), the pressure oil in the hydraulic chamber A (B) on the high pressure side flows. The flow is set to flow in the channel 4 and the channel 5.

  The switching valve 2A is connected to the open / close control valve (poppet valve) C and the open / close control valve (poppet valve) D to the flow passages 4 and 5 through which the hydraulic oil from the hydraulic chambers A and B can move. Connected to the tip of the auxiliary hydraulic tank 7 is a flow path 6 through which the pressure oil that has passed through the opening / closing control valve D can move to the opening / closing control valve (poppet valve) E. Only when the solenoid D2 of the solenoid valve D1 connected to the opening / closing control valve D is excited, the pressure oil in the hydraulic chamber A (B) on the high pressure side is free to pass through the opening / closing control valve D; The pressure oil that moves to the opening / closing control valve D via the switching valve 2A receives the command from the controller 8 (energized), and passes through the opening / closing control valve D when the solenoid D2 is excited. Although it goes to the E side, since the opening / closing control valve E is normally closed by the solenoid valve E1, the pressure oil that has passed through the opening / closing control valve D moves to the auxiliary hydraulic tank 7.

  The solenoid C2 of the solenoid valve C1 connected to the opening / closing control valve C is in a state in which the pressure oil that has entered the flow path 4 is allowed to freely pass through the opening / closing control valve C only when excited, and enters the flow path 4. When the solenoid valve C1 receives a command from the controller 8 (energized) and the solenoid C2 is excited, the pressurized oil passes through the open / close control valve C and can flow into the low pressure side hydraulic chamber B (A). To do.

  Only when the solenoid E2 of the solenoid valve E1 connected to the open / close control valve E is excited, the pressure oil that has entered the flow path 6 from the auxiliary hydraulic tank 7 is in a state of freely passing through the open / close control valve E, The pressure oil that has entered the flow path 6 from the auxiliary hydraulic tank 7 receives a command (energized) by the solenoid valve E1 from the controller 8 and passes through the open / close control valve E when the solenoid E2 is energized. A state in which it can flow into the chamber B (A) is set.

  For example, the measured values of the pressure gauges 11 and 11 installed in both the hydraulic chambers A and B are transmitted to the controller 8, and the controller 8 changes the pressure in one of the hydraulic chambers A (B) from increasing to decreasing. When this is detected (FIG. 2- (b)), an energization command is transmitted to the solenoid valve D1, the solenoid D2 is excited, and the open / close control valve D is opened (FIG. 2- (c)). The controller 8 reverses the direction of interlayer deformation based on measurement values sent from a displacement meter or the like that measures the amount of interlayer deformation of the frame 20 and measurement values that are found by changes in the pressure difference between the hydraulic chambers A and B. Sometimes it is judged.

  When the open / close control valve D is opened (FIG. 2- (c)), the pressure oil that has entered the flow path 5 from within the hydraulic chamber A (B) on the high pressure side passes through the open / close control valve D to assist the hydraulic pressure. It moves to the tank 7 and is temporarily stored. The pressure in the hydraulic chamber A (B) on the high pressure side drops due to the movement of the pressure oil in the hydraulic chamber A (B) on the high pressure side to the auxiliary hydraulic tank 7 and the pressure in the hydraulic chamber A (B) on the high pressure side. And the pressure of the auxiliary hydraulic tank 7 reaches a state of equilibrium.

  When the controller 8 detects that the pressures in the hydraulic chamber A (B) and the auxiliary hydraulic tank 7 are balanced, the controller 8 cuts off the energization to the solenoid valve D1, and at the same time transmits an energization command to the solenoid valve C1, and the solenoid C2 And the open / close control valve C is opened while closing the open / close control valve D (FIG. 2- (d)). By opening the opening / closing control valve C, the pressure oil moves freely between the hydraulic chambers A and B, the pressure difference between the hydraulic chambers A and B is eliminated, and an equilibrium state is reached.

  When the pressures in the hydraulic chambers A and B are balanced, the controller 8 cuts off the energization to the solenoid valve C1, and then sends an energization command to the solenoid valve E1 to excite the solenoid E2, thereby opening and closing the control valve C. Is closed, and the open / close control valve E is opened (FIG. 2- (e)). At the time of closing the open / close control valve C, the interlayer deformation starts to move slightly in the opposite direction. Therefore, when the open / close control valve C is closed, the hydraulic chamber A ( The pressure in the hydraulic chamber B (A), which was on the low pressure side, slightly increases from the pressure in B). For this reason, the switching valve 2A is switched, and the flow path 6 through which the pressure oil that has passed through the opening / closing control valve E from the auxiliary hydraulic tank 7 flows is connected to the hydraulic chamber B (A). Accordingly, when the opening / closing control valve E is opened, the pressure oil in the auxiliary hydraulic tank 7 having a relatively higher pressure than in the hydraulic chamber B (A) flows through the flow path 6 until the pressure in the auxiliary hydraulic tank 7 is balanced. The pressure in the hydraulic chamber B (A) is increased.

  FIG. 9 shows the hydraulic damper 1 and each of the hydraulic dampers 1 when each of the on-off control valves C to E of the hydraulic damper 1 shown in FIG. 1 is controlled due to the occurrence of a pressure difference between the hydraulic chambers A and B (hydraulic fluctuation). An example of connection with the open / close control valves C to E is shown. Also in this example, when one of the hydraulic chambers A and B is on the high pressure side, the hydraulic chamber A (B) from the high pressure side hydraulic chamber A (B) A switching valve 2A for flowing pressure oil to the opening / closing control valve D and the opening / closing control valve C is connected.

  In this case, since the controller 8 does not control the on-off control valves C, D, and E, the on-off control valves C, D, and E have switching valves C3, D3, and D4 instead of the solenoid valves C1 to E1 in FIG. Connected. The switching valve C3 and the switching valve D3 maintain the open / close control valves C and D in a closed state by blocking the flow of pressure oil for operating the open / close control valves C and D by a spring force in a normal state. doing. The open / close control valve E opens when the switching valves C3 and D3 are in a normal state and the pressure in the auxiliary hydraulic tank 7 exceeds the pressure in the high-pressure side hydraulic chamber A (B). The pressure oil in 7 flows into the hydraulic chamber A (B) on the high pressure side.

  When the pressure in the buffer 9 connected to the flow path 5 in parallel with the open / close control valve D exceeds the pressure in the high pressure side hydraulic chamber A (B), the switching valve D3 can open / close the open / close control valve D. It switches to the state which makes the flow of the pressure oil to make free against the force of a spring, and opens and closes the on-off control valve D (FIG.2- (c)). In the example of FIG. 9, the combination of the switching valve D3, the buffer 9 for operating the switching, and the check valve 9A for supplying pressure oil thereto corresponds to the solenoid valve D1 in the example of FIG. To work.

  While the pressure in one of the hydraulic chambers A (B) is rising due to the movement of the piston 3 in one direction, the pressure oil in the hydraulic chamber A (B) on the high pressure side passes through the check valve 9A from the flow path 5. To enter the buffer 9. When the moving direction of the piston 3 is reversed, the pressure in the high pressure side hydraulic chamber A (B) decreases accordingly, but a check valve is provided in the flow path connecting the buffer 9 and the high pressure side hydraulic chamber A (B). Since 9A is provided, the pressure in the buffer 9 is prevented from decreasing, so that the pressure in the buffer 9 exceeds the pressure in the hydraulic chamber A (B) on the high pressure side. As a result, the switching valve D3 is switched to open the opening / closing control valve D (FIG. 2- (c)), and the pressure oil in the hydraulic chamber A (B) on the high pressure side passes through the opening / closing control valve D from the flow path 5. To the auxiliary hydraulic tank 7.

  When the pressure oil in the high pressure side hydraulic chamber A (B) and the pressure in the auxiliary hydraulic tank 7 are balanced with the movement of the pressure oil in the high pressure side hydraulic chamber A (B) to the auxiliary hydraulic tank 7, The switching valve D4, which is connected to the switching valve D3 and prevents the flow from the buffer 9 through the switching valve D3 in the normal state, switches to a state in which the flow from the buffer 9 becomes free, and the pressure oil from the buffer 9 is switched to the switching valve. It flows into the accumulator 10 connected to D4. When the pressure in the buffer 9 drops due to the movement of the pressure oil from the buffer 9 to the accumulator 10 and equilibrates with the pressure in the hydraulic chamber A (B) on the high pressure side, the switching valve D3 is in a normal state by the force of the spring. The opening / closing control valve D is closed.

  When the pressure oil in the buffer 9 further flows into the accumulator 10 and the pressure drops and falls below the pressure in the high pressure side hydraulic chamber A (B), the switching valve D3 returns to the normal position, and the switching valve C3 Switching is performed to open / close the control valve C (FIG. 2- (d)). Opening the opening / closing control valve C frees the movement of the pressure oil between the hydraulic chambers A and B through the opening / closing control valve C, and the pressure between the hydraulic chambers A and B is balanced. When the pressure between the hydraulic chambers A and B is balanced, the switching valve C3 starts to return to the normal state by the force of the spring. The switching valve C3 closes the back pressure flow path of the open / close control valve C with a small amount of movement so that the back pressure flow path of the open / close control valve E is connected when it is completely restored to the normal state. Since it is set, the switching control valve C is first closed while the switching valve C3 is returning to the normal state.

  At this time, since the piston 3 has started to move slightly in the opposite direction, when the open / close control valve C returns to the closed state, the pressure in the hydraulic chamber B (A), which was on the low pressure side until immediately before, is increased to just before. The switching valve 2A is switched to be higher than the hydraulic chamber A (B) that is on the side, and the flow path 6 from the open / close control valve E is connected to the hydraulic chamber B (A) that is on the low pressure side until just before. After that, when the switching valve C3 is completely returned to the normal position, the back pressure flow path that has kept the open / close control valve E closed is connected to the hydraulic chamber B (A) that was on the low pressure side until just before. The Since the pressure in the auxiliary hydraulic tank 7 is higher than the pressure in the hydraulic chamber B (A), the open / close control valve E is opened, and the pressure oil in the auxiliary hydraulic tank 7 passes through the flow path 6 to the hydraulic chamber B (A). Flows in. At this time, since the open / close control valve C is in a closed state, the pressure in the hydraulic chamber B (A) is increased until the pressure in the auxiliary hydraulic tank 7 is balanced.

  FIG. 10 shows that the buffer 9 and the check valve 9A are connected in parallel to the opening / closing control valve C in the hydraulic circuit shown in FIG. 8, and the accumulator 10 that can communicate with the buffer 9 is connected to the buffer 9 in series. 9 is connected between the solenoid valve C1 attached to the accumulator 10 and the accumulator 10 to form a hydraulic circuit in which the hydraulic circuit shown in FIG. 8 and the hydraulic circuit shown in FIG. 9 are combined. An example is shown.

  In the example of FIG. 10, the solenoid D2 of the solenoid valve D1 attached to the opening / closing control valve D and the solenoid E2 of the solenoid valve E1 attached to the opening / closing control valve E are kept closed in a normal state (when no power is supplied). The solenoid C2 of C1 is kept open as shown in the figure when not energized, that is, in a state where the pressure oil from the buffer 9 can flow to the switching valve D3 side. The solenoid C2 is placed in a normally energized state to prevent the flow of pressure oil from the buffer 9 toward the switching valve D3, and is illustrated when it is in a non-energized state upon receiving a command from the controller 8. Thus, the flow of the pressure oil from the buffer 9 toward the switching valve D3 is set to a state where it can occur.

  In this case, when the pressure of either one of the hydraulic chambers A and B changes from rising to lowering, the solenoid valve D1 is energized by a command from the controller 8 and when the solenoid D2 is excited, the opening / closing control valve D is opened. Then, the pressure oil in the hydraulic chamber A (B) on the high pressure side moves to the auxiliary hydraulic tank 7. Thereafter, when the pressure in the auxiliary hydraulic tank 7 and the pressure in the hydraulic chamber A (B) on the high pressure side are balanced, energization to the solenoid D2 is interrupted by a command from the controller 8 and at the same time, When the energization is also cut off, the pressure stored in the buffer 9 exceeds the pressure in the hydraulic chamber A (B) on the high pressure side, the switching valve D3 switches against the spring, and the opening / closing control valve C opens. . By opening the opening / closing control valve C, the pressure difference between the hydraulic chambers A and B is eliminated.

  When the pressure difference between the hydraulic chambers A and B is resolved, the solenoid C2 is energized to shut off the flow of pressure oil through the buffer 9, and the control valve C is closed. The opposite hydraulic chamber B (A) is relatively high in pressure, and the switching valve 2A is switched. Subsequently, when the solenoid E2 is energized, the open / close control valve E is opened, the pressure oil in the auxiliary hydraulic tank 7 flows into the hydraulic chamber B (A), and the pressure in the hydraulic chamber B (A) is changed to the auxiliary hydraulic tank 7. It will be increased to equilibrate with the pressure of

  In the example of FIG. 10, the opening / closing of each of the opening / closing control valves C to E is controlled completely automatically and has a simpler configuration than the hydraulic circuit shown in FIG. 9 that does not depend on the controller 8. Since the solenoid C2 is opened when the supply is interrupted and the solenoid C2 is opened, the automatic hydraulic switching circuit similar to that of Patent Document 2 is switched, so that the switching control similar to that of Patent Document 2 is guaranteed. In the example of FIG. 10 as well, the timing of energizing the solenoids C2, D2, and E2 is based on the measured values from the pressure gauges 11 and 11 installed in the hydraulic chambers A and B. Energization may be performed based on the value.

  When the hydraulic damper 1 is incorporated in the actual frame 20, the load (resistance force) generated by the hydraulic damper 1 does not become excessive, and the damper body and the frame 20 are not damaged, that is, the pressure between the hydraulic chambers A and B. In order to prevent the difference from exceeding a certain value, the relief valve 12 may be connected to a flow path that directly connects the hydraulic chambers A and B as shown in FIG. FIG. 11- (b) shows a schematic diagram of the load-deformation relationship when the relief valve 12 is actuated. When the relief valve 12 is actuated, the timing at which the load becomes maximum (point P in FIG. 11- (b)). It can be seen that does not coincide with the timing at which the interlayer deformation reaches the maximum value. Therefore, if the open / close control valve is controlled based on the pressure in the hydraulic chamber of the damper, energy absorption efficiency may be lost. In order to avoid the loss of energy absorption efficiency, the control of the open / close control valve should not be performed in a state where the load generated by the hydraulic damper 1 is larger than the operating load Fr of the relief valve 12.

  FIG. 12 shows a case where a relief valve 12 is connected in parallel with the switching valve 2A (flow path 4) in the hydraulic circuit shown in FIG. 8 to release an excess pressure difference between the hydraulic chambers A and B in each direction. There is no problem when the open / close control valve is controlled based on the measured value of the interlayer deformation. However, when the control is performed based on the pressure in the hydraulic chambers A and B, the pressure difference between the hydraulic chambers A and B is If it is larger than the operating load Fr, the algorithm may be changed to an algorithm (program) that does not control the open / close control valve.

  FIG. 13 shows an example in which the relief valve 12 is connected in parallel to the switching valve 2 </ b> A (flow path 4) in the hydraulic circuit shown in FIG. 9 and the relief valve 13 is connected between the buffer 9 and the accumulator 10. Since the pressure of the buffer 9 is controlled by the relief valve 13 so as not to exceed the operating load Fr of the relief valve 12, the opening / closing control is performed by the pressure in the buffer 9 exceeding the pressure in the hydraulic chamber A (B) on the high pressure side. The opening operation of the valves D, C, E is avoided.

  FIG. 14 shows an example in which the relief valve 12 is connected in parallel to the switching valve 2A (flow path 4) in the hydraulic circuit shown in FIG. 10 and the relief valve 13 is connected between the buffer 9 and the accumulator 10. Also in this case, even if the solenoid C2 is opened at the time of power failure, the pressure in the buffer 9 is controlled by the relief valve 13 so that the pressure in the buffer 9 does not exceed the operating load Fr of the relief valve 12, so that the pressure in the buffer 9 is high. The operation of opening the on-off control valve C due to exceeding the pressure in the hydraulic chamber A (B) on the side is avoided.

1 …… Hydraulic damper,
2 ... Cylinder,
A ... Hydraulic chamber, B ... Hydraulic chamber,
2A …… Switching valve,
C: Open / close control valve, C1: Solenoid valve, C2: Solenoid, C3: Switching valve,
D: Open / close control valve, D1: Solenoid valve, D2: Solenoid, D3: Switching valve, D4: Switching valve,
E …… Open / close control valve, E1 …… Solenoid valve, E2 …… Solenoid,
3 ... Piston, 3A ... Piston rod,
4 …… Flow path (between hydraulic chambers A and B),
5 ... Flow path (between one hydraulic chamber and auxiliary hydraulic tank), 6 ... Flow path (between auxiliary hydraulic tank and other hydraulic chamber),
7 ... auxiliary hydraulic tank, 8 ... controller,
9: Buffer, 9A: Check valve, 10: Accumulator, 11: Pressure gauge,
12: Relief valve (flow path), 13: Relief valve (between buffer and accumulator),
20 ... frame, 21 ... brace.

Claims (4)

A cylinder, a piston that reciprocates in the cylinder, hydraulic chambers provided on both sides of the piston, and an open / close control valve that is connected to a flow path that connects both the hydraulic chambers and can be switched between an open state and a closed state In the hydraulic damper
The hydraulic damper includes an auxiliary hydraulic tank that is connected to the cylinder and can store pressure oil, and an open / close control valve that is connected between the auxiliary hydraulic tank and the hydraulic chambers and can be switched between an open state and a closed state. Prepared,
While the piston is moving in either direction, the full open / close control valve is closed to generate pressure in the hydraulic chamber on one side, and when the direction of movement of the piston is reversed, it becomes the high pressure side. Opening one of the open / close control valves connecting the one hydraulic chamber and the auxiliary hydraulic tank to move the pressure oil in the one hydraulic chamber to the auxiliary hydraulic tank;
After that, the open / close control valve is closed, and the open / close control valve that connects the hydraulic chambers is opened to release the pressure in the hydraulic chamber on the high pressure side, thereby eliminating the pressure difference between the hydraulic chambers. Then, the open / close control valve is closed and the open / close control valve that connects the auxiliary hydraulic tank and the other hydraulic chamber on the opposite side of the one side is opened to open the auxiliary hydraulic pressure. A control method for a hydraulic damper on / off control valve, wherein a series of operations for moving the pressure oil in a tank to the other hydraulic chamber and closing the open / close control valve is performed.   A hydraulic damper for use in the control method for the on / off control valve according to claim 1, comprising an electric drive means for operating the on / off control valve to be opened / closed by an external current supply. Hydraulic damper.   2. A hydraulic damper for use in the control method for the on / off control valve according to claim 1, comprising hydraulic drive means for operating the on / off control valve based on the occurrence of a pressure difference between the two hydraulic chambers. Hydraulic damper characterized by being A hydraulic damper used in the control method of the on / off control valve according to claim 1, wherein an electric drive means for operating the on / off control valve to open / close by supplying current from the outside, and a pressure between the two hydraulic chambers A hydraulic damper comprising hydraulic drive means for operating opening / closing of the opening / closing control valve based on occurrence of a difference.

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