Patent Grant
11808158
The present invention relates to an electrohydrostatic actuation system, a hydraulic circuit of an electrohydrostatic actuation system for a steam turbine, and to a steam turbine system including the same.
In Patent Literature 1, there is disclosed a fail-safe actuation system configured so that, in a working circuit configured to actuate, by means of a hydraulic pressure, an actuator for use to drive a valve of a steam turbine or the like, the actuator is moved to a safety position in a case of a failure. In Patent Literature 2, there is disclosed a configuration using a trip solenoid valve and a logic valve in order to quickly close a valve of a steam turbine or the like.
As described above, in the actuator configured to drive the valve of the steam turbine or the like, a mechanism for achieving emergency shut-off of the valve has various modes, but particularly in an electrohydrostatic actuation system, it is required to use a solenoid valve to achieve the emergency shut-off. It is required to stably actuate the mechanism for achieving the emergency shut-off with a simple configuration.
When electric power to a hydraulic pump configured to generate a hydraulic pressure is lost, it is required to activate a fail-safe function to promptly bring a valve element into a valve closed state. At this time, it is required to protect the hydraulic pump from hydraulic fluid refluxed to the hydraulic pump.
The hydraulic pump is sometimes operated beyond the rated output due to overload, and a servo motor is sometimes overheated at this time. It is required to control a pump displacement in accordance with an external load, and to operate under a state in which a load to the hydraulic pump is suppressed.
The hydraulic fluid is sealed in a completely closed system, and hence the hydraulic fluid is provided under a state in which a circulation amount of the hydraulic fluid is small and thus the temperature is liable to rise. Thus, there are problems in that the viscosity or other performance of the hydraulic fluid is decreased early, and efficiency of the electrohydrostatic actuation system is decreased. Accordingly, it is required to prevent the performance of the hydraulic fluid from being deteriorated.
The present invention has an object to provide an electrohydrostatic actuation system including an emergency shut-off circuit to be actuated stably with a simple configuration. The present invention has another object to provide an electrohydrostatic actuation system including a hydraulic circuit configured to protect a hydraulic pump at the time of fail-safe shut-off. The present invention has further another object to provide an electrohydrostatic actuation system capable of performing, in accordance with an external load, an operation under a state in which a load to a hydraulic pump is suppressed. The present invention has further another object to provide an electrohydrostatic actuation system in which performance of hydraulic fluid is stabilized.
In order to solve the above-mentioned problems, according to the present invention, there is provided an electrohydrostatic actuation system including: a hydraulic cylinder including a piston to which a valve element biased by a return spring is connected, a first chamber, and a second chamber; a hydraulic pump configured to supply hydraulic fluid to the first chamber or the second chamber; an electric motor configured to drive the hydraulic pump; a shuttle valve configured to establish communication to a downstream side under a state in which a hydraulic pressure generated by the hydraulic pump is maintained; a solenoid valve configured to receive the hydraulic pressure via the shuttle valve as a pilot pressure; and a logic valve including a first port configured to receive the pilot pressure from the solenoid valve, and a second port communicated to the first chamber of the hydraulic cylinder, wherein, when the solenoid valve is brought to a de-energized state, the pilot pressure of the logic valve is released, and the logic valve causes the hydraulic fluid in the first chamber communicated to the second port to flow into the second chamber so that emergency shut-off of the valve element is achieved by the return spring.
According to the present invention, the electrohydrostatic actuation system including an emergency shut-off circuit to be actuated stably with a simple configuration can be provided. Further, the electrohydrostatic actuation system including a hydraulic circuit configured to protect the hydraulic pump at the time of fail-safe shut-off can be provided. Still further, the electrohydrostatic actuation system capable of performing, in accordance with an external load, an operation under a state in which a load to the hydraulic pump is suppressed can be provided. Yet further, the electrohydrostatic actuation system in which performance of the hydraulic fluid is stabilized can be provided.
Now, modes for carrying out the present invention are described in detail with reference to the accompanying drawings.
The electrohydrostatic actuation system of Example 1 of the present invention includes a pump/motor unit 10 in a hydraulic circuit. The pump/motor unit 10 includes a hydraulic pump 21 formed of a radial piston pump, and the hydraulic pump 21 is to be driven and controlled by a servo motor M (electric motor) capable of performing driving in both forward and reverse directions. The configuration of the radial piston pump may be a pump of other types, such as an axial piston pump or a gear pump.
A pressure accumulator 22 is included in the hydraulic circuit. The pressure accumulator 22 always maintains a pressurizing state so that the hydraulic circuit can be filled with the hydraulic fluid even when some leakage from the hydraulic circuit occurs. The hydraulic circuit includes two check valves 23A and 23B for cavitation prevention, and the hydraulic fluid from the pressure accumulator 22 is supplied to the hydraulic circuit via the check valves 23A and 23B. Further, the check valves 23A and 23B keep the pressure constant, and hence occurrence of cavitation is prevented. The pressure accumulator 22 may also be a pressure pump with a reservoir tank.
A hydraulic cylinder 24 serving as a hydraulic actuator and a piston 25 are included. The piston 25 including a piston rod 25R is arranged inside the hydraulic cylinder 24. The inside of the hydraulic cylinder 24 is divided by this piston 25 into two chambers, namely, a first chamber 24A and a second chamber 24B. The piston 25 is driven when the hydraulic pump 21 supplies the hydraulic fluid to the first chamber 24A or the second chamber 24B of the hydraulic cylinder 24, or when the hydraulic pump 21 collects the hydraulic fluid from the second chamber 24B or the first chamber 24A. One side of the piston rod 25R is connected to the piston 25, and another side of the piston rod 25R is connected to a steam valve (valve element) (not shown). When the piston rod 25R is driven in both extending and contracting directions, the steam valve can be opened or closed. Further, a return spring 26 is included between the steam valve and the hydraulic cylinder 24, and the steam valve is biased in a valve closing direction by the return spring 26. The hydraulic cylinder 24 may be a hydraulic actuator of other types, for example, a hydraulic motor.
Relief valves 27A and 27B are included in the hydraulic circuit. The relief valves 27A and 27B release the hydraulic fluid to fluid passages 9a and 9b being return pipes, respectively, when the pressure of the hydraulic circuit exceeds a set pressure, to thereby prevent the pressure in the hydraulic circuit from overrising. A filter and bypass valve 28 is connected to a fluid passage 9c being a return pipe of the hydraulic pump 21 as a valve for filtering the hydraulic fluid. Further, a radiator and cooling fan 29 serving as an active cooling circuit configured to cool the hydraulic fluid may be provided in series to the filter and bypass valve 28.
Next, a normal valve opening operation is described. Originally, the entire hydraulic circuit is equally pressurized by the pressure accumulator 22 to a defined pressure which is, as an example, a pressure of about 0.5 MPa. The pressure is set here as 0.5 MPa, but the pressure can be set to any other pressure values. When a controller (not shown) outputs a command to open the steam valve, the pump/motor unit 10 discharges high-pressure hydraulic fluid from a port A (discharge port) of the hydraulic pump 21. The hydraulic fluid passes through a fluid passage 1a to be supplied to the first chamber 24A of the hydraulic cylinder 24. Simultaneously, the hydraulic fluid present in the second chamber 24B of the hydraulic cylinder 24 passes through a fluid passage 1b to flow toward the hydraulic pump 21, and is sucked through a port B of the hydraulic pump 21.
When the pressure generated by the hydraulic pump 21 is not large enough to surpass an external force, for example, a pressure caused by steam or the return spring 26, the piston 25 does not move. However, when the pressure reaches a pressure surpassing the external force, the piston 25 moves so that the steam valve is opened. The hydraulic cylinder 24 is a double-rod cylinder having equal pressure receiving areas on both sides thereof, and hence an inflow amount of the hydraulic fluid to the first chamber 24A is the same as an outflow amount thereof from the second chamber 24B. The hydraulic pump 21 is controlled so that a desired opening degree of the steam valve can be obtained, and further, the desired opening degree can be maintained.
Next, a normal valve closing operation is described. When the return spring 26 is to close the steam valve by its biasing force, a reflux at a large flow rate of hydraulic fluid may be caused to close the valve at an excessive speed, but the speed to close the valve can be controlled when the pressure to be generated by the pump/motor unit 10 is controlled. That is, the speed to close the steam valve is controlled under a state in which the pressure generated by the pump/motor unit 10 acts against the biasing force. Then, in order to obtain an optimum valve closing speed, the hydraulic pump 21 sucks the hydraulic fluid flowing from the first chamber 24A to the port A, and simultaneously discharges the hydraulic fluid through the port B (discharge port) to supply the hydraulic fluid to the second chamber 24B. At the time of the normal valve opening and closing operations, the pressure controlled by the pump/motor unit 10 is lower than set pressures of the relief valves 27A and 27B, and hence the relief valves 27A and 27B are kept closed.
Next, an emergency shut-off circuit of Example 1 of the present invention is described. The hydraulic circuit of Example 1 includes a shuttle valve 11 (first valve), at least one trip solenoid valve 12A, 12B (second valve, described as “solenoid valve 12” as a representative thereof), and at least one logic valve 13A, 13B (third valve, described as “logic valve 13” as a representative thereof).
The shuttle valve 11 is a valve of a so-called “back-to-back check” type including therein two valve elements, for example, poppets or balls, and a preloaded spring between those two valve elements. The hydraulic fluid in a fluid passage 2a branched from the fluid passage 1a is input to the shuttle valve 11 via one valve element, and further, the hydraulic fluid in a fluid passage 2b branched from the fluid passage 1b is input to the shuttle valve 11 via the other valve element. Then, with the preloaded spring in the shuttle valve 11, an inlet side of the input having a higher pressure of those two input pressures is communicated to an outlet side (downstream side). For example, when the steam valve is to be opened, the pressure of the hydraulic fluid in the fluid passage 2a is higher than the pressure of the hydraulic fluid in the fluid passage 2b, and hence the hydraulic fluid from the fluid passage 2a flows into the shuttle valve 11 from the inlet side, and is communicated to the outlet side. However, when the steam valve is to be closed, the strength of the steam valve closing operation is sometimes intentionally increased by bringing the pressure of the hydraulic fluid in the fluid passage 2b to be relatively higher than the pressure of the hydraulic fluid in the fluid passage 2a. In such a case, the hydraulic fluid from the fluid passage 2b flows into the shuttle valve 11 from the inlet side, and is communicated to the outlet side. That is, the shuttle valve 11 is one valve configured to communicate, to the downstream side, the hydraulic fluid having a higher pressure between the pressure of the hydraulic fluid to be supplied and the pressure of the hydraulic fluid to be collected. The outlet side of the shuttle valve 11 is connected to a fluid passage 2ab, and the fluid passage 2ab (trip line) is further branched into two paths, which are applied as pilot pressures to the trip solenoid valves 12A and 12B, respectively. As described above, through use of the shuttle valve 11, an optimum pressure can be selected from two hydraulic sources. Further, the shuttle valve 11 allows integration and simplification of the hydraulic circuit as compared to a case in which two check valves are used, and hence production cost and time and effort can be reduced.
The trip solenoid valves 12A and 12B are normally energized, and the pilot pressures from the shuttle valve 11 pass through a fluid passage 1ac and a fluid passage 2bc via the trip solenoid valves 12A and 12B to be applied to the two logic valves 13A and 13B, respectively.
The two logic valves 13A and 13B are each a valve configured to close by an internal return spring, and each include a first port to which the fluid passage 1ac or the fluid passage 2bc for supplying the pilot pressure from the trip solenoid valve 12A or 12B is connected. Further, the two logic valves 13A and 13B each include a second port to which a fluid passage 3a branched from the fluid passage 1a is connected. That is, the second port is communicated to the first chamber 24A of the hydraulic cylinder 24 via the fluid passage 1a and the fluid passage 3a. Further, the logic valve 13A and the logic valve 13B are arranged in parallel to the first chamber 24A. A fluid passage 3b through which the hydraulic fluid from the fluid passage 3a is caused to flow is connected to the logic valve 13A, and the fluid passage 3b is connected to the logic valve 13B. A fluid passage 3c connected to the fluid passage 1b is further connected to the logic valve 13B. The hydraulic fluid flowing through this fluid passage 3b flows to the fluid passage 3c via the logic valve 13B. Then, a sum of the pilot pressure and the biasing force of the internal return spring acts against the pressure from the hydraulic cylinder 24, thereby closing the fluid passage 3a from the first chamber 24A of the hydraulic cylinder 24 connected to the second ports of the logic valves 13A and 13B.
When an emergency shut-off signal is received from the controller (not shown), the trip solenoid valve 12 is brought to a de-energized state, and the pilot pressure applied to the logic valve 13 is released. Then, the logic valve 13 is opened when the pressure from the hydraulic cylinder 24 surpasses the biasing force of the internal return spring. Thus, the fluid passage 1a, the fluid passage 3a, the fluid passage 3b, the fluid passage 3c, and the fluid passage 1b which are connected to the first chamber 24A are communicated to each other. With this communication, the hydraulic fluid in the first chamber 24A can pass through the fluid passage 1a, the fluid passage 3a, the fluid passage 3b, the fluid passage 3c, and the fluid passage 1b to directly and quickly flow into the second chamber 24B. With this quick inflow of the hydraulic fluid, the steam valve biased in the valve closing direction by the biasing force of the return spring 26 can be quickly closed.
As described above, the hydraulic fluid in the first chamber 24A is rapidly refluxed from the first chamber 24A to the second chamber 24B without passing through the hydraulic pump 21, and hence the piston rod 25R can quickly move to quickly close the steam valve. Unless the trip solenoid valve 12 is brought to a de-energized state, the pilot pressure in the trip line is maintained by the shuttle valve 11, and hence the logic valve 13 is kept closed.
As described above, the emergency shut-off circuit of Example 1 includes the shuttle valve 11, the trip solenoid valve 12, and the logic valve 13, thereby being capable of quickly closing the steam valve. In particular, the pilot pressure in the trip line is confined by the shuttle valve 11, and hence the logic valve 13 is kept closed. Thus, there is provided such an excellent effect that the emergency shut-off circuit can be actuated stably with a simple configuration.
A fail-safe shut-off and pump/motor unit protection circuit of Example 2 of the present invention is described.
First, with reference to
Next, a normal valve opening operation of Example 2 is described. Originally, the entire hydraulic circuit is equally pressurized by the pressure accumulator 22 to a defined pressure which is, as an example, a pressure of about 0.5 MPa. The pressure is set here as 0.5 MPa, but the pressure can be set to any other pressure values. When the controller (not shown) outputs the command to open the steam valve, the pump/motor unit 10 discharges high-pressure hydraulic fluid from the port A of the hydraulic pump 21. The hydraulic fluid passes through the fluid passage 1a, and part thereof passes through a fluid passage 4a branched from the fluid passage 1a to be applied to the logic valve 15 as a pilot pressure. A differential pressure from the pump/motor unit 10 to the hydraulic cylinder 24 is positive, and hence the hydraulic fluid in the fluid passage 1a after the branch passes through the fuse valve 14, and part thereof is branched to pass through a fluid passage 5a. Then, the hydraulic fluid passes through a throttle valve 20 provided in the fluid passage 5a, and is connected to the logic valve 15. Further, the hydraulic fluid in the fluid passage 1a after the branch is supplied to the first chamber 24A of the hydraulic cylinder 24. Simultaneously, the hydraulic fluid present in the second chamber 24B of the hydraulic cylinder 24 passes through the fluid passage 1b to flow toward the hydraulic pump 21, and is collected through the port B of the hydraulic pump 21.
Next, with reference to
The fuse valve 14 is configured to block, when the flow rate of the hydraulic fluid flowing through the fluid passage 1a becomes larger than a set value, the flow of the hydraulic fluid to the pump/motor unit 10 from the first chamber 24A on the load side of the hydraulic cylinder 24. Simultaneously, the port A of the hydraulic pump 21 loses pressure, and hence the pilot pressure applied to the logic valve 15 is lost. Thus, the logic valve 15 communicates the fluid passage 5a branched from the fluid passage 1a and a fluid passage 5b connected to the fluid passage 1b to each other. That is, the fluid passage 1a, the fluid passage 5a, the fluid passage 5b, and the fluid passage 1b which are on the downstream side (first chamber 24A side) of the fuse valve 14 are communicated to each other, and thus the hydraulic fluid in the first chamber 24A passes through the logic valve 15 to flow to the second chamber 24B, thereby being capable of achieving the fail-safe shut-off of the steam valve. The fuse valve 14 blocks the fluid passage 1a connected to the hydraulic pump 21, and thus the hydraulic fluid cannot flow back to the hydraulic pump 21. Accordingly, simultaneously with the fail-safe shut-off, the pump/motor unit 10 can be protected without applying an overload to the hydraulic pump 21. The speed to close the steam valve at this time can be adjusted by using the throttle valve 20.
When the fail-safe shut-off and pump/motor unit protection circuit is not included, in a case in which the pump/motor unit 10 loses electric power, the hydraulic fluid flows back to the hydraulic pump 21, and the hydraulic pump 21 is over-rotated. Further, there are problems in that cavitation and mechanical wear occur. However, provision of the fail-safe shut-off and pump/motor unit protection circuit of Example 2, there is such an effect that the occurrence of cavitation and mechanical wear can be prevented.
As described above, provision of the fail-safe shut-off and pump/motor unit protection circuit of Example 2, when electric power to the hydraulic pump 21 configured to generate a hydraulic pressure is lost, allows the valve element to be promptly brought into a valve closed state. At this time, there is provided such an excellent effect that the hydraulic pump 21 can be protected from the hydraulic fluid refluxed to the hydraulic pump 21.
A displacement switching circuit for a hydraulic pump 31 of Example 3 of the present invention is described.
First, with reference to
Originally, the entire hydraulic circuit is equally pressurized by the pressure accumulator 22 to a defined pressure which is, as an example, a pressure of about 0.5 MPa. The pressure is set here as 0.5 MPa, but the pressure can be set to any other pressure values. When the controller (not shown) outputs the command to open the steam valve, the pump/motor unit 30 discharges high-pressure hydraulic fluid from the port A of the hydraulic pump 31. The hydraulic fluid passes through the fluid passage 1a, and part thereof passes through the fluid passage 4a branched from the fluid passage 1a to be applied to the sequence valve 16. The fluid passage 4a is further connected to the four-port, two-position pilot-operated directional control valve 17, and the hydraulic fluid is applied as a pilot pressure of the four-port, two-position pilot-operated directional control valve 17. Further, the hydraulic fluid in the fluid passage 1a after the branch is supplied to the first chamber 24A of the hydraulic cylinder 24. Simultaneously, the hydraulic fluid present in the second chamber 24B of the hydraulic cylinder 24 passes through the fluid passage 1b to flow toward the hydraulic pump 31, and is collected through the port B of the hydraulic pump 31.
Next, the configuration of the hydraulic circuit for the displacement switching as in Example 3 of the present invention is described. A fluid passage 6a, a fluid passage 6b, and a fluid passage 6c are connected to the sequence valve 16. The fluid passage 6a is branched from the fluid passage 4a and includes a restrictor. The fluid passage 6b is connected to the fluid passage 4a and the four-port, two-position pilot-operated directional control valve 17. The fluid passage 6c is connected to a fluid passage 9a. Further, the fluid passage 4a, the fluid passage 6b connected to the sequence valve 16, and a fluid passage 7c are connected to the four-port, two-position pilot-operated directional control valve 17. The fluid passage 7c is connected to a displacement pilot line (fluid passage 7a and fluid passage 7b) to be described later and to a fluid passage 9b.
Next, the actuation of the displacement switching at the time when the pressure of the hydraulic fluid is smaller than the predetermined set value is described. When the pressure of the hydraulic fluid from the port A of the hydraulic pump 31 becomes lower than a set pressure of the sequence valve 16, the sequence valve 16 is actuated so that the fluid passage 6c connected to the fluid passage 9a (drain line) and the fluid passage 6b connected to the four-port, two-position pilot-operated directional control valve 17 are connected to each other. With this actuation, a pilot line pressure of the four-port, two-position pilot-operated directional control valve 17 is decreased. At this time, the four-port, two-position pilot-operated directional control valve 17 is actuated so that the fluid passage 4a branched from the fluid passage 1a to which the port A at an original position is connected and the displacement pilot line (fluid passage 7a) of the hydraulic pump 31 at which the displacement is maximum (max) are connected to each other. Thus, the displacement from the hydraulic pump 31 is increased.
Next, with reference to
As described above, provision of the displacement switching circuit of Example 3 allows the displacement of the hydraulic pump 31 to be controlled in accordance with the external load, thereby providing such an excellent effect that an operation can be performed under a state in which the load to the hydraulic pump 31 is suppressed.
A hydraulic fluid cooling circulation circuit of Example 4 of the present invention is described.
First, with reference to
Next, a normal valve opening operation as in Example 4 is described. Originally, the entire hydraulic circuit is equally pressurized by the pressure accumulator 22 to a defined pressure which is, as an example, a pressure of about 0.5 MPa. The pressure is set here as 0.5 MPa, but the pressure can be set to any other pressure values. When the controller (not shown) outputs the command to open the steam valve, the pump/motor unit 10 discharges high-pressure hydraulic fluid from the port A of the hydraulic pump 21. The hydraulic fluid passes through the fluid passage 1a, and part thereof passes through the fluid passage 4a branched from the fluid passage 1a to be applied to the pilot-assisted open relief valve 18 as a pilot pressure. Then, the hydraulic fluid in the fluid passage 1a after the branch is supplied to the first chamber 24A of the hydraulic cylinder 24. At the time of the normal valve opening operation, the pressure controlled by the hydraulic pump 21 is lower than the set pressure of the relief valve 27A, and hence the relief valve 27A is kept closed.
The fluid passage 4a, a fluid passage 8a, and a fluid passage 8b are connected to the pilot-assisted open relief valve 18. The fluid passage 8a is connected to the fluid passage 1b. The fluid passage 8b is connected to the fluid passage 9b. During the steam valve opening operation, the pilot-assisted open relief valve 18 is brought into a valve open state by the pilot pressure from the port A supplied through the fluid passage 4a so that the fluid passage 8a (fluid passage 1b) and the fluid passage 8b (fluid passage 9b) are communicated to each other. The hydraulic fluid flowing from the second chamber 24B of the hydraulic cylinder 24 through the fluid passage 1b toward the port B is blocked by the check valve 19 provided on the downstream side (hydraulic cylinder 24 side) of the port B, and thus does not directly flow into the port B. However, the pilot-assisted open relief valve 18 is open, and hence the hydraulic fluid in the fluid passage 1b passes through the fluid passage 8a, the pilot-assisted open relief valve 18, and the fluid passage 8b to flow through the fluid passage 9b (drain line). Then, the hydraulic fluid flows through the fluid passage 9b, is mixed with the hydraulic fluid supplied from the pressure accumulator 22, passes through the check valve 23B for cavitation prevention, and is sucked through the port B of the hydraulic pump 21.
Next, with reference to
It is known from experiments performed so far that the temperature of the hydraulic fluid around the pressure accumulator 22 is generally lower than the hydraulic fluid temperature around the hydraulic pump 21. This is useful for keeping the temperature of the hydraulic fluid in the system to be low (keeping the hydraulic fluid to have an appropriate degree of viscosity) and ensuring an appropriate efficiency of the system.
As described above, provision of the hydraulic fluid cooling circulation circuit of Example 4, even under a state in which the circulation amount of the hydraulic fluid is small and thus the temperature is liable to rise, there is such an excellent effect that the viscosity or other performance of the hydraulic fluid can be prevented from being deteriorated.
Example 5 of the present invention shows a configuration including the emergency shut-off circuit and the fail-safe shut-off and pump/motor unit protection circuit. That is, Example 5 includes the configurations of Examples 1 and 2 described above.
In Example 5, the hydraulic circuit includes, in addition to the shuttle valve 11, the trip solenoid valve 12, and the logic valve 13 of Example 1, the fuse valve 14 and the logic valve 15. Supply of hydraulic fluid to those shuttle valve 11, trip solenoid valve 12, and logic valve 13 is similar to that in Example 1, and hence detailed description thereof is omitted. Further, the normal valve closing operation of Example 5 is also similar to that in Example 1, and hence detailed description thereof is omitted. Further, actuations of the fuse valve 14 and the logic valve 15 are similar to those in Example 2, and hence detailed description thereof is omitted.
At the time of fail-safe shut-off in which the pump/motor unit 10 loses electric power, the trip solenoid valve 12 is still energized, and the logic valve 13 is brought into a closed state by the pilot pressure via the shuttle valve 11. Accordingly, the hydraulic fluid does not flow through the logic valve 13.
As in Example 5, provision of the emergency shut-off circuit and the fail-safe shut-off and pump/motor unit protection circuit, allows to handle both of the emergency shut-off and the fail-safe shut-off. Further, there is provided such an excellent effect that, at the time of fail-safe shut-off, the hydraulic pump 21 can be protected from the hydraulic fluid refluxed to the hydraulic pump 21.
Example 6 of the present invention shows a configuration including the emergency shut-off circuit and the displacement switching circuit. That is, Example 6 includes the configurations of Examples 1 and 3 described above.
In Example 6, the hydraulic circuit includes, in addition to the shuttle valve 11, the trip solenoid valve 12, and the logic valve 13 of Example 1, the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17. The hydraulic pump 31 is of a variable displacement type. Supply of hydraulic fluid to those shuttle valve 11, trip solenoid valve 12, and logic valve 13 is similar to that in Example 1, and hence detailed description thereof is omitted. Further, the normal valve closing operation of Example 6 is also similar to that in Example 1, and hence detailed description thereof is omitted. Further, actuations of the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17 are similar to those in Example 3, and hence detailed description thereof is omitted.
As in Example 6, provision of the emergency shut-off circuit and the displacement switching circuit allows to handle the emergency shut-off, and further, the displacement of the hydraulic pump 31 is controlled in accordance with the external load, thereby providing such an excellent effect that the operation can be performed under a case in which the load to the hydraulic pump 31 is suppressed.
Example 7 of the present invention shows a configuration including the emergency shut-off circuit and the hydraulic fluid cooling circulation circuit. That is, Example 7 includes the configurations of Examples 1 and 4 described above.
In Example 7, the hydraulic circuit includes, in addition to the shuttle valve 11, the trip solenoid valve 12, and the logic valve 13 of Example 1, the pilot-assisted open relief valve 18, and the check valve 19. Supply of hydraulic fluid to those shuttle valve 11, trip solenoid valve 12, and logic valve 13 is similar to that in Example 1, and hence detailed description thereof is omitted. Further, the normal valve closing operation of Example 7 is also similar to that in Example 1, and hence detailed description thereof is omitted. Further, actuations of the pilot-assisted open relief valve 18 and the check valve 19 are similar to those in Example 4, and hence detailed description thereof is omitted.
As in Example 7, provision of the emergency shut-off circuit and the hydraulic fluid cooling circulation circuit allows to handle the emergency shut-off, and further, there is provided such an excellent effect that, even under a state in which the circulation amount of the hydraulic fluid is small and thus the temperature is liable to rise, the viscosity or other performance of the hydraulic fluid can be prevented from being deteriorated.
Example 8 of the present invention shows a configuration including an emergency shut-off circuit, a fail-safe shut-off circuit and pump/motor unit protection, and a displacement switching circuit. That is, Example 8 includes the configurations of Examples 1 to 3 described above.
In Example 8, the hydraulic circuit includes, in addition to the shuttle valve 11, the trip solenoid valve 12, and the logic valve 13 of Example 1, the fuse valve 14, the logic valve 15, the sequence valve 16, and the four-port, two-position pilot-operated directional control valve 17. The hydraulic pump 31 is of a variable displacement type. Supply of hydraulic fluid to those shuttle valve 11, trip solenoid valve 12, and logic valve 13 is similar to that in Example 1, and hence detailed description thereof is omitted. Further, the normal valve closing operation of Example 8 is also similar to that in Example 1, and hence detailed description thereof is omitted. Further, actuations of the fuse valve 14 and the logic valve 15 are similar to those in Example 2, and actuations of the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17 are similar to those in Example 3. Thus, detailed description thereof is omitted.
As in Example 8, provision of the emergency shut-off circuit, the fail-safe shut-off and pump/motor unit protection circuit, and the displacement switching circuit allows to handle both of the emergency shut-off and the fail-safe shut-off. Further, at the time of fail-safe shut-off, the hydraulic pump 31 can be protected from the hydraulic fluid refluxed to the hydraulic pump 31. Further, the displacement of the hydraulic pump 31 is controlled in accordance with the external load, thereby providing such an excellent effect that the operation can be performed under a state in which the load to the hydraulic pump 31 is suppressed.
Example 9 of the present invention shows a configuration including an emergency shut-off circuit, a fail-safe shut-off and pump/motor unit protection circuit, and a hydraulic fluid cooling circulation circuit. That is, Example 9 includes the configurations of Examples 1, 2, and 4 described above.
In Example 9, the hydraulic circuit includes, in addition to the shuttle valve 11, the trip solenoid valve 12, and the logic valve 13 of Example 1, the fuse valve 14, the logic valve 15, the pilot-assisted open relief valve 18, and the check valve 19. Supply of hydraulic fluid to those shuttle valve 11, trip solenoid valve 12, and logic valve 13 is similar to that in Example 1, and hence detailed description thereof is omitted. Further, the normal valve closing operation of Example 9 is also similar to that in Example 1, and hence detailed description thereof is omitted. Further, actuations of the fuse valve 14 and the logic valve 15 are similar to those in Example 2, and actuations of the pilot-assisted open relief valve 18 and the check valve 19 are similar to those in Example 4. Thus, detailed description thereof is omitted.
As in Example 9, provision of the emergency shut-off circuit, the fail-safe shut-off circuit, and the hydraulic fluid cooling circulation circuit allows to handle both of the emergency shut-off and the fail-safe shut-off. Further, at the time of fail-safe shut-off, the hydraulic pump 21 can be protected from the hydraulic fluid refluxed to the hydraulic pump 21. Further, even under a state in which the circulation amount of the hydraulic fluid is small and thus the temperature is liable to rise, there is provided such an excellent effect that the viscosity or other performance of the hydraulic fluid can be prevented from being deteriorated.
Example 10 of the present invention shows a configuration including the emergency shut-off circuit, the fail-safe shut-off and pump/motor unit protection circuit, the displacement switching circuit, and the hydraulic fluid cooling circulation circuit. That is, Example 10 includes the configurations of Examples 1 to 4 described above.
In Example 10, the hydraulic circuit includes, in addition to the shuttle valve 11, the trip solenoid valve 12, and the logic valve 13 of Example 1, the fuse valve 14 and the logic valve 15 of Example 2. Further, the hydraulic circuit includes the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17 of Example 3, and the pilot-assisted open relief valve 18 and the check valve 19 of Example 4. The hydraulic pump 31 is of a variable displacement type. Supply of hydraulic fluid to those shuttle valve 11, trip solenoid valve 12, and logic valve 13 is similar to that in Example 1, and hence detailed description thereof is omitted. Further, the normal valve closing operation of Example 10 is also similar to that in Example 1, and hence detailed description thereof is omitted. Further, actuations of the fuse valve 14 and the logic valve 15 are similar to those in Example 2, and actuations of the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17 are similar to those in Example 3. Further, actuations of the pilot-assisted open relief valve 18 and the check valve 19 are similar to those in Example 4. Thus, detailed description thereof is omitted.
As in Example 10, provision of the emergency shut-off circuit, the fail-safe shut-off and pump/motor unit protection circuit, the displacement switching circuit, and the hydraulic fluid cooling circulation circuit allow to handle both of the emergency shut-off and the fail-safe shut-off. Further, at the time of fail-safe shut-off, the hydraulic pump 31 can be protected from the hydraulic fluid refluxed to the hydraulic pump 31. Further, the displacement of the hydraulic pump 31 is controlled in accordance with the external load, thereby being capable of performing the operation under a state in which the load to the hydraulic pump 31 is suppressed. Further, even under a state in which the circulation amount of the hydraulic fluid is small and thus the temperature is liable to rise, there is provided such an excellent effect that the viscosity or other performance of the hydraulic fluid can be prevented from being deteriorated.
Example 11 of the present invention shows a configuration including the emergency shut-off circuit, the displacement switching circuit, and the hydraulic fluid cooling circulation circuit. That is, Example 11 includes the configurations of Examples 1, 3, and 4 described above.
In Example 11, the hydraulic circuit includes the shuttle valve 11, the trip solenoid valve 12, and the logic valve 13 of Example 1. Further, the hydraulic circuit includes the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17 of Example 3, and the pilot-assisted open relief valve 18 and the check valve 19 of Example 4. The hydraulic pump 31 is of a variable displacement type. Supply of hydraulic fluid to those shuttle valve 11, trip solenoid valve 12, and logic valve 13 is similar to that in Example 1, and hence detailed description thereof is omitted. Further, the normal valve closing operation of Example 11 is also similar to that in Example 1, and hence detailed description thereof is omitted. Further, actuations of the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17 are similar to those in Example 3. Further, actuations of the pilot-assisted open relief valve 18 and the check valve 19 are similar to those in Example 4. Thus, detailed description thereof is omitted.
As in Example 11, provision of the emergency shut-off circuit, the displacement switching circuit, and the hydraulic fluid cooling circulation circuit allows to handle the emergency shut-off. Further, the displacement of the hydraulic pump 31 is controlled in accordance with the external load, thereby being capable of performing the operation under a state in which the load to the hydraulic pump 31 is suppressed. Further, even under a state in which the circulation amount of the hydraulic fluid is small and thus the temperature is liable to rise, there is provided such an excellent effect that the viscosity or other performance of the hydraulic fluid can be prevented from being deteriorated.
Example 12 of the present invention shows a configuration including the fail-safe shut-off and pump/motor unit protection circuit and the displacement switching circuit. That is, Example 12 includes the configurations of Examples 2 and 3 described above.
In Example 12, the hydraulic circuit includes the fuse valve 14 and the logic valve 15 in Example 2, and the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17 of Example 3. The hydraulic pump 31 is of a variable displacement type. Supply of hydraulic fluid to those fuse valve 14 and logic valve 15 is similar to that in Example 2, and hence detailed description thereof is omitted. Further, actuations of the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17 are similar to those in Example 3. Thus, detailed description thereof is omitted.
As in Example 12, provision of the fail-safe shut-off circuit and pump/motor unit protection and the displacement switching circuit allows to handle the fail-safe shut-off. Further, at the time of fail-safe shut-off, the hydraulic pump 31 can be protected from the hydraulic fluid refluxed to the hydraulic pump 31. Further, the displacement of the hydraulic pump 31 is controlled in accordance with the external load, thereby providing such an excellent effect that the operation can be performed under a state in which the load to the hydraulic pump 31 is suppressed.
Example 13 of the present invention shows a configuration including the fail-safe shut-off and pump/motor unit protection circuit and the hydraulic fluid cooling circulation circuit. That is, Example 13 includes the configurations of Examples 2 and 4 described above.
In Example 13, the hydraulic circuit includes the fuse valve 14 and the logic valve 15 of Example 2, and the pilot-assisted open relief valve 18 and the check valve 19. Actuations of the fuse valve 14 and the logic valve 15 are similar to those in Example 2. Further, actuations of the pilot-assisted open relief valve 18 and the check valve 19 are similar to those in Example 4. Thus, detailed description thereof is omitted.
As in Example 13, provision of the fail-safe shut-off and pump/motor unit protection circuit and the hydraulic fluid cooling circulation circuit allows to handle the fail-safe shut-off. Further, at the time of fail-safe shut-off, the hydraulic pump 21 can be protected from the hydraulic fluid refluxed to the hydraulic pump 21. Further, even under a state in which the circulation amount of the hydraulic fluid is small and thus the temperature is liable to rise, there is provided such an excellent effect that the viscosity or other performance of the hydraulic fluid can be prevented from being deteriorated.
Example 14 of the present invention shows a configuration including the fail-safe shut-off and pump/motor unit protection circuit, the displacement switching circuit, and the hydraulic fluid cooling circulation circuit. That is, Example 14 includes the configurations of Examples 2 to 4 described above.
In Example 14, the hydraulic circuit includes the fuse valve 14 and the logic valve 15 of Example 3, the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17 of Example 3, and the pilot-assisted open relief valve 18 and the check valve 19 of Example 4. The hydraulic pump 31 is of a variable displacement type. Actuations of the fuse valve 14 and the logic valve 15 are similar to those in Example 2, and actuations of the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17 are similar to those in Example 3. Further, actuations of the pilot-assisted open relief valve 18 and the check valve 19 are similar to those in Example 4. Thus, detailed description thereof is omitted.
As in Example 14, provision of the fail-safe shut-off and pump/motor unit protection circuit, the displacement switching circuit, and the hydraulic fluid cooling circulation circuit allows to handle the fail-safe shut-off. Further, at the time of fail-safe shut-off, the hydraulic pump 31 can be protected from the hydraulic fluid refluxed to the hydraulic pump 31. Further, the displacement of the hydraulic pump 31 is controlled in accordance with the external load, thereby being capable of performing the operation under a state in which the load to the hydraulic pump 31 is suppressed. Further, even under a state in which the circulation amount of the hydraulic fluid is small and thus the temperature is liable to rise, there is provided such an excellent effect that the viscosity or other performance of the hydraulic fluid can be prevented from being deteriorated.
Example 15 of the present invention shows a configuration including the displacement switching circuit and the hydraulic fluid cooling circulation circuit. That is, Example 15 includes the configurations of Examples 3 and 4 described above.
In Example 15, the hydraulic circuit includes the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17 of Example 3, and the pilot-assisted open relief valve 18 and the check valve 19 of Example 4. The hydraulic pump 31 is of a variable displacement type. Actuations of the sequence valve 16 and the four-port, two-position pilot-operated directional control valve 17 are similar to those in Example 3. Further, actuations of the pilot-assisted open relief valve 18 and the check valve 19 are similar to those in Example 4. Thus, detailed description thereof is omitted.
As in Example 15, provision of the displacement switching circuit and the hydraulic fluid cooling circulation circuit allows to control the displacement of the hydraulic pump 31 in accordance with the external load, thereby being capable of performing the operation under a state in which the load to the hydraulic pump 31 is suppressed. Further, even under a state in which the circulation amount of the hydraulic fluid is small and thus the temperature is liable to rise, there is provided such an excellent effect that the viscosity or other performance of the hydraulic fluid can be prevented from being deteriorated.
Preferred Examples 1 to 15 of the present invention are described above, but the present invention is not limited to those Examples and can be modified and changed variously within the scope of the gist thereof.
This application claims the benefit of priority from Japanese Patent Application No. 2019-167187, filed on Sep. 13, 2019, the content of which is incorporated herein by reference.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2019-167187 | Sep 2019 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2020/017941 | 4/27/2020 | WO |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2021/049093 | 3/18/2021 | WO | A |
| Number | Name | Date | Kind |
|---|---|---|---|
| 3713291 | Kubik | Jan 1973 | A |
| 3864911 | Gellatly | Feb 1975 | A |
| 4147325 | McGee | Apr 1979 | A |
| 4807517 | Daeschner | Feb 1989 | A |
| 5137253 | Frey | Aug 1992 | A |
| 6892534 | Silva | May 2005 | B2 |
| 8341956 | Makino | Jan 2013 | B2 |
| 8753067 | Shindo | Jun 2014 | B2 |
| 8997473 | Olson | Apr 2015 | B2 |
| 10578227 | Goll | Mar 2020 | B2 |
| 10851772 | Junginger | Dec 2020 | B2 |
| 10871080 | Tsunekawa et al. | Dec 2020 | B2 |
| 11428246 | Miyajima | Aug 2022 | B2 |
| 20150152887 | Helbig et al. | Jun 2015 | A1 |
| 20150334918 | Daining | Nov 2015 | A1 |
| 20180172177 | Goll | Jun 2018 | A1 |
| 20180216485 | Tsunekawa et al. | Aug 2018 | A1 |
| Number | Date | Country |
|---|---|---|
| 108374696 | Aug 2018 | CN |
| 20 25 836 | Dec 1971 | DE |
| 10 2013 216 790 | Feb 2015 | DE |
| 2930410 | Oct 2015 | EP |
| 2943459 | Aug 1999 | JP |
| 2018-123732 | Aug 2018 | JP |
| 6746511 | Aug 2020 | JP |
| Entry |
|---|
| An Office Action mailed by China National Intellectual Property Administration dated Feb. 2, 2023, which corresponds to Chinese Patent Application No. 202080023131.5 and is related to U.S. Appl. No. 17/441,663; with English language translation. |
| International Search Report issued in PCT/JP2020/017941; dated Jun. 30, 2020. |
| An Office Action; “Notice of Reasons for Refusal,” mailed by the Japanese Patent Office dated Jan. 5, 2023, which corresponds to Japanese Patent Application No. 2019-167187 and is related to U.S. Appl. No. 17/441,663; with English language translation. |
| Communication Pursuant to Rule 164(1) EPC issued by the European Patent Office dated Jul. 25, 2023, which corresponds to EP20863439.4-1012 and is related to U.S. Appl. No. 17/441,663. |
| Number | Date | Country | |
|---|---|---|---|
| 20220145770 A1 | May 2022 | US |
