Patent Application
20140345265
1. Field of the Invention
The present invention relates to a hydraulic drive system.
2. Background Information
Work machines, such as a hydraulic excavator or a wheel loader, are equipped with a hydraulic cylinder. Hydraulic fluid discharged from a hydraulic pump is supplied to the hydraulic cylinder through a hydraulic circuit. For example, Japanese National Publication of International Patent Application No. 2009-511831 describes a work machine equipped with a hydraulic closed circuit for supplying hydraulic fluid to the hydraulic cylinders. Kinetic energy and potential energy of the members driven by the hydraulic cylinder are regenerated due to the hydraulic circuit being a closed circuit. As a result, fuel consumption of a driving source for driving the hydraulic pump may be reduced.
A charge circuit is often installed in the closed hydraulic circuit. The charge circuit is provided for replenishing an amount of hydraulic fluid corresponding to oil leakage from the hydraulic pump. A charge pump and a relief valve are provided in the charge circuit. The charge pump is normally a fixed displacement pump and is driven by a driving source, such as an engine. The relief valve regulates the hydraulic pressure (referred to below as “charge pressure”) in the charge circuit. When the flow rate of the hydraulic fluid supplied to the hydraulic pump is insufficient, the hydraulic pressure in the hydraulic closed circuit falls below the charge pressure and hydraulic fluid is supplied from the charge circuit to the hydraulic closed circuit.
The hydraulic closed circuit described above is desirably provided in a hydraulic circuit for which the sufficient regeneration of kinetic energy and potential energy is expected. As a result, the hydraulic closed circuit is often provided independently of a normal hydraulic circuit. For example, in the case of a hydraulic excavator, a boom cylinder is driven by the hydraulic closed circuit. Alternatively, in the case of a wheel loader, a lift cylinder is driven by the hydraulic closed circuit. In these cases, the hydraulic closed circuit is not operated when the vehicle is traveling. As a result, power consumption in the charge pump is mostly lost.
The use of a variable displacement pump as the charge pump may be considered to reduce the loss of power consumption in the abovementioned charge pump. In this case, loss of power consumption in the charge pump may be reduced by changing the discharge flow rate of the charge pump to zero when the hydraulic closed circuit is not operating. However, variable displacement pumps are more expensive than fixed displacement pumps. As a result, there is a problem in that the cost of a work machine increases when a variable displacement pump is used for the charge pump.
Moreover, a check valve is provided in the abovementioned hydraulic closed circuit to prohibit a reverse flow of the hydraulic fluid. The check valve is disposed between a hydraulic pump and a hydraulic cylinder in the hydraulic closed circuit. For example, the check valve is disposed between the hydraulic pump and the boom cylinder in the hydraulic closed circuit when the hydraulic cylinder is a boom cylinder in a hydraulic excavator. Because a superimposed load of the bucket or the load from the deadweight of the working implement acts on the boom cylinder, hydraulic pressure for supporting such a load (referred to below as “holding pressure”) is produced in a flowpath between the boom cylinder and the check valve. When hydraulic fluid is supplied to the boom cylinder in this state, the hydraulic fluid discharged from the hydraulic pump is used first to raise the hydraulic pressure between the hydraulic pump and the check valve to the holding pressure. Then, when the hydraulic pressure in the flowpath between the hydraulic pump and the check valve equals or exceeds the holding pressure, the check valve is opened and the hydraulic fluid is supplied to the boom cylinder. Consequently, the operation of the boom cylinder starts. Because there is no return oil from the boom cylinder to the hydraulic pump before the operation of the boom cylinder starts, all of the hydraulic fluid supplied to the hydraulic pump is supplied from the charge circuit. Therefore, the charge pump requires only enough capacity to be able to supply a flow rate of the hydraulic fluid when raising the pressure in this way. Conversely, the existing hydraulic pressure between the hydraulic pump and the boom cylinder while the boom cylinder is in operation reaches the required pressure to drive the boom cylinder. As a result, the charge pump may be able to supply the hydraulic fluid at a flow rate that is less than the abovementioned flow rate when raising the pressure. Therefore, when the capacity of the charge pump is set on the basis of when the pressure is raised as described above, hydraulic fluid at an excessive flow rate is produced during the operation of the boom cylinder. The hydraulic fluid at the excessive flow rate is exhausted from the charge flowpath to a hydraulic fluid tank. In this way, when the capacity of the charge pump is set on the basis of when the pressure is raised as described above, hydraulic fluid at a high flow rate is wastefully exhausted from the charge flowpath. Further, if the capacity of the charge pump is high, the loss of power consumption in the charge pump in the abovementioned state when the hydraulic closed circuit is not in operation also increases.
An aspect of the present invention is to provide a hydraulic drive system that reduces power consumption loss in the charge pump.
The hydraulic drive system according to a first aspect of the present invention is provided with a main pump, a hydraulic cylinder, a hydraulic fluid flowpath, a check valve, a charge circuit, an operating member, an operating state determining unit, a discharge pressure reducing unit, a discharge pressure control unit, an accumulator, and a one-way valve. The main pump has a first hydraulic pump and a second hydraulic pump that discharge hydraulic fluid. The hydraulic cylinder is driven by hydraulic fluid discharged from the main pump. The hydraulic fluid flowpath connects the first hydraulic pump and the second hydraulic pump to the hydraulic cylinder. The hydraulic fluid flowpath configures a closed circuit between the first hydraulic pump and the hydraulic cylinder. The check valve is disposed between the main pump and the hydraulic cylinder in the hydraulic fluid flowpath. The check valve allows the flow of hydraulic fluid from the main pump to the hydraulic cylinder and prohibits the flow of hydraulic fluid from the hydraulic cylinder to the main pump. The charge circuit has a charge flowpath and a charge pump. The charge flowpath is connected between the main pump and the check valve in the hydraulic fluid flowpath. The charge pump discharges hydraulic fluid into the charge flowpath. The charge circuit replenishes the hydraulic fluid flowpath with hydraulic fluid when the hydraulic pressure in the hydraulic fluid flowpath is lower than the charge pressure. The operating member is a member for operating the hydraulic cylinder. The operating state determining unit determines whether the hydraulic cylinder is in operation or not in operation. A discharge pressure reducing unit reduces the discharge pressure of a charge pump. A discharge pressure control unit controls the discharge pressure reducing unit while the hydraulic cylinder in not in operation to reduce the discharge pressure of the charge pump to a low pressure lower than a normal pressure. The normal pressure is the discharge pressure of the charge pump when the hydraulic cylinder is in operation. An accumulator is connected to a charge flowpath. A one-way valve is disposed between the accumulator and the charge pump. The one-way valve allows the flow of hydraulic fluid from the charge pump to the accumulator and prohibits the flow of hydraulic fluid from the accumulator to the charge pump.
The hydraulic drive system according to a second aspect of the present invention is related to the hydraulic drive system of the first aspect, and further includes an accumulated pressure detecting unit and an accumulated pressure determining unit. The accumulated pressure detecting unit detects an accumulated pressure of the accumulator. The accumulated pressure determining unit determines whether the accumulated pressure of the accumulator is equal to or less than a first setting pressure. The discharge pressure control unit changes the discharge pressure of the charge pump from the low pressure to the normal pressure when the accumulated pressure of the accumulator is equal to or less than the first setting pressure while the hydraulic cylinder is not in operation.
The hydraulic drive system according to a third aspect of the present invention is related to the hydraulic drive system of the second aspect, wherein the accumulated pressure determining unit determines whether the accumulated pressure of the accumulator is equal to or greater than a second setting pressure. The second setting pressure is higher than the first setting pressure. The discharge pressure control unit returns the discharge pressure of the charge pump to the normal pressure from the normal pressure when the accumulated pressure of the accumulator recovers from a pressure equal to or less than the first setting pressure to a pressure equal to or greater than the second setting pressure while the hydraulic cylinder is not in operation.
The hydraulic drive system according to a fourth aspect of the present invention is related to the hydraulic drive system of the second or third aspect, and further includes a pump control unit. The pump control unit controls the discharge flow rate of the main pump on the basis of an operating position of the operating member. The operating state determining unit determines whether the hydraulic cylinder is in operation or not in operation on the basis of the operating position of the operating member. The accumulated pressure determining unit determines whether the accumulated pressure of the accumulator is equal to or less than a third setting pressure. The pump control unit conducts a standby control even if an operation to start the discharge of hydraulic fluid from the main pump is conducted by the operating member when the accumulated pressure of the accumulator is equal to or less than the third setting pressure. The standby control is a control for not allowing the start of the discharge of hydraulic fluid from the main pump until the accumulated pressure of the accumulator is greater than the third setting pressure.
The hydraulic drive system according to a fifth aspect of the present invention is related to the fourth aspect, wherein the third setting pressure is a pressure that is equal to or greater than the first setting pressure.
A hydraulic drive system according to a sixth aspect of the present invention is related to the hydraulic drive system of the fourth or fifth aspect, and further includes a display device that displays the fact that the standby control is being executed.
A hydraulic drive system according to a seventh aspect of the present invention is related to any one of the hydraulic drive system of the first to sixth aspects, wherein the operating state determining unit determines that the hydraulic cylinder is not in operation when the operating member is being held in a neutral position for a time period equal to or greater than a certain time period.
The hydraulic drive system according to an eighth aspect of the present invention is related to any one of the first to seventh aspects, wherein the charge flowpath has a first charge flowpath and a second charge flowpath. The first charge flowpath is connected to the charge pump. The second charge flowpath is connected to the first charge flowpath via the one-way valve. The discharge pressure reducing unit reduces the hydraulic pressure in the first charge flowpath.
The discharge pressure of the charge pump is reduced to the low pressure when the hydraulic cylinder is not in operation in the hydraulic drive system according to the first aspect of the present invention. As a result, power consumption loss in the charge pump may be reduced. Further, the replenishment of the hydraulic fluid flowpath with hydraulic fluid is made possible with hydraulic fluid discharged from the charge pump and hydraulic fluid stored in the accumulator when the pressure in the hydraulic fluid flowpath between the main pump and the check valve is raised up to the holding pressure. As a result, the charge pump may be made smaller in comparison to when the hydraulic fluid flowpath is replenished with hydraulic fluid only from the charge pump. As a result, power consumption loss in the charge pump may be further reduced. The flow of hydraulic fluid stored in the accumulator to the charge pump is prohibited when the charge pump is stopped due to the one-way valve. As a result, a reduction in the accumulated pressure of the accumulator may be suppressed.
Conversely, hydraulic fluid stored in the accumulator leaks gradually from sliding parts of the first hydraulic pump even if the hydraulic cylinder is not in operation. As a result, when the discharge pressure of the charge pump is maintained at the low pressure for a long period of time, the accumulated pressure of the accumulator falls due to the reduction of the hydraulic fluid stored in the accumulator over a period of time. In this state, there is a concern that aeration or cavitation may occur in the first hydraulic pump due to the shortage of hydraulic fluid to replenish the hydraulic fluid flowpath from the charge circuit when the hydraulic cylinder is in operation. Accordingly, the discharge pressure control unit changes the discharge pressure of the charge pump from the low pressure to the normal pressure when the accumulated pressure of the accumulator is equal to or less than the first setting pressure while the hydraulic cylinder is not in operation in the hydraulic drive system according to the second aspect of the present invention. As a result, a reduction in the accumulated pressure of the accumulator may be suppressed even when the hydraulic cylinder is maintained in a non-operating state for a long period of time. Specifically, the occurrence of aeration or of cavitation in the first hydraulic pump may be suppressed when operation of the hydraulic cylinder is started.
The discharge pressure of the charge pump is returned from the normal pressure to the low pressure when the accumulated pressure of the accumulator recovers to be equal to or greater than the second setting pressure in the hydraulic drive system according to the third aspect of the present invention. As a result, a reduction in the accumulated pressure of the accumulator is suppressed and power consumption loss in the charge pump may be reduced.
The discharge of hydraulic fluid from the main pump is not started until the accumulated pressure of the accumulator exceeds the third setting pressure even if the operating member is operated in the hydraulic drive system according to the fourth aspect of the present invention. As a result, the occurrence of aeration or of cavitation in the first hydraulic pump may be suppressed.
The discharge of hydraulic fluid from the main pump may be started in a state in which a required amount of hydraulic fluid is stored in the accumulator in the hydraulic drive system according to the fifth aspect of the present invention.
An operator may be notified that the main pump will not start due to the execution of the standby control in the hydraulic drive system according to the sixth aspect of the present invention.
The mistaken determination that the hydraulic cylinder is not in operation when the hydraulic cylinder is actually in operation, such as when the operating member temporarily passes through the neutral position, may be prevented in the hydraulic drive system according to the seventh aspect of the present invention.
The discharge pressure reducing unit reduces the pressure in the first charge flowpath in the hydraulic drive system according to the eighth aspect of the present invention. As a result, the discharge pressure of the charge pump is reduced.
A hydraulic drive system according to an exemplary embodiment of the present invention is explained hereinbelow with reference to the drawings.
The engine 11 drives the main pump 10. The engine 11 is a diesel engine, for example, and the output of the engine 11 is controlled by adjusting an injection amount of fuel from a fuel injection pump 21. The adjustment of the fuel injection amount is performed by the engine controller 22 controlling the fuel injection device 21. An actual rotation speed of the engine 11 is detected by a rotation speed sensor 23, and a detection signal is input into the engine controller 22 and the pump controller 24.
The main pump 10 is driven by the engine 11 to discharge hydraulic fluid. The main pump 10 includes a first hydraulic pump 12 and a second hydraulic pump 13. Hydraulic fluid discharged from the main pump 10 is supplied to the hydraulic cylinder 14 via the flowpath switching valve 16.
The first hydraulic pump 12 is a variable displacement hydraulic pump. The discharge flow rate of the first hydraulic pump 12 is controlled by controlling a tilt angle of the first hydraulic pump 12. The tilt angle of the first hydraulic pump 12 is controlled by a first pump-flow-rate control unit 25. The first pump-flow-rate control unit 25 controls the discharge flow rate of the first hydraulic pump 12 by controlling the tilt angle of the first hydraulic pump 12 on the basis of a command signal from the pump controller 24. The first hydraulic pump 12 is a two-directional discharge hydraulic pump. Specifically, the first hydraulic pump 12 has a first pump port 12a and a second pump port 12b. The first hydraulic pump 12 is switchable between a first discharge state and a second discharge state. The first hydraulic pump 12 sucks in hydraulic fluid from the second pump port 12b and discharges hydraulic fluid from the first pump port 12a in the first discharge state. The first hydraulic pump 12 sucks in hydraulic fluid from the first pump port 12a and discharges hydraulic fluid from the second pump port 12b in the second discharge state.
The second hydraulic pump 13 is a variable displacement hydraulic pump. The discharge flow rate of the second hydraulic pump 13 is controlled by controlling the tilt angle of the second hydraulic pump 13. The tilt angle of the second hydraulic pump 13 is controlled by a second pump-flow-rate control unit 26. The second pump-flow-rate control unit 26 controls the discharge flow rate of the second hydraulic pump 13 by controlling the tilt angle of the second hydraulic pump 13 on the basis of a command signal from the pump controller 24. The second hydraulic pump 13 is a two-directional discharge hydraulic pump. Specifically, the second hydraulic pump 13 has a first pump port 13a and a second pump port 13b. The second hydraulic pump 13 is switchable between a first discharge state and a second discharge state in the same way as the first hydraulic pump 12. The second hydraulic pump 13 sucks in hydraulic fluid from the second pump port 13b and discharges hydraulic fluid from the first pump port 13a in the first discharge state. The second hydraulic pump 12 sucks in hydraulic fluid from the first pump port 13a and discharges hydraulic fluid from the second pump port 13b in the second discharge state.
The hydraulic cylinder 14 is driven by hydraulic fluid discharged from the main pump 10. The hydraulic cylinder 14 drives working implements such as a boom, an arm, or a bucket. The hydraulic cylinder 14 includes a cylinder rod 14a and a cylinder tube 14b. The inside of the cylinder tube 14b is partitioned by the cylinder rod 14a into a first chamber 14c and a second chamber 14d. The hydraulic cylinder 14 has a first cylinder port 14e and a second cylinder port 14f. The first cylinder port 14e communicates with the first chamber 14c. The second cylinder port 14f communicates with the second chamber 14d. The hydraulic cylinder 14 is switchable between a state in which hydraulic fluid is supplied to the second cylinder port 14f and hydraulic fluid is exhausted from the first cylinder port 14e, and a state in which hydraulic fluid is supplied to the first cylinder port 14e and hydraulic fluid is exhausted from the second cylinder port 14f. The hydraulic cylinder 14 expands and contracts by switching between the supply and exhaust of hydraulic fluid to and from the first chamber 14c and the second chamber 14d. Specifically, the hydraulic cylinder 14 expands due to hydraulic fluid being supplied to the first chamber 14c via the first cylinder port 14e, and hydraulic fluid being exhausted from the second chamber 14d via the second cylinder port 14f. The hydraulic cylinder 14 contracts due to hydraulic fluid being supplied to the second chamber 14d via the second cylinder port 14f, and hydraulic fluid being exhausted from the first chamber 14c via the first cylinder port 14e. A pressure receiving area of the cylinder rod 14a in the first chamber 14c is greater than a pressure receiving area of the cylinder rod 14a in the second chamber 14d. Therefore, when the hydraulic cylinder 14 is expanded, more hydraulic fluid is supplied to the first chamber 14c than is exhausted from the second chamber 14d. When the hydraulic cylinder 14 is contracted, more hydraulic fluid is exhausted from the first chamber 14c than is supplied to the second chamber 14d.
The hydraulic fluid flowpath 15 connects the first hydraulic pump 12 and the second hydraulic pump 13 to the hydraulic cylinder 14. Specifically, the hydraulic fluid flowpath 15 includes a first flowpath 17 and a second flowpath 18. The first flowpath 17 connects the first pump port 12a of the first hydraulic pump 12 with the first cylinder port 14e. The first flowpath 17 connects the first pump port 13a of the second hydraulic pump 13 with the first cylinder port 14e. The second flowpath 18 connects a second pump port 12b of the first hydraulic pump 12 with the second cylinder port 14f. The first flowpath has a first cylinder flowpath 31 and a first pump flowpath 33. The second flowpath 18 has a second cylinder flowpath 32 and a second pump path 34. The first cylinder flowpath 31 is connected to the first chamber 14c of the hydraulic cylinder 14 via the first cylinder port 14e. The second cylinder flowpath 32 is connected to the second chamber 14d of the hydraulic cylinder 14 via the second cylinder port 14f. The first pump path 33 is a path for supplying hydraulic fluid to the first chamber 14c of the hydraulic cylinder 14 via the first cylinder path 31, or for recovering hydraulic fluid from the first chamber 14c of the hydraulic cylinder 14 via the first cylinder path 31. The first pump path 33 is connected to the first pump port 12a of the first hydraulic pump 12. The first pump path 33 is connected to the first pump port 13a of the second hydraulic pump 13. Therefore, hydraulic fluid is supplied to the first pump flowpath 33 from both the first hydraulic pump 12 and the second hydraulic pump 13. The second pump path 34 is a path for supplying hydraulic fluid to the second chamber 14d of the hydraulic cylinder 14 via the second cylinder path 32, or for recovering hydraulic fluid from the second chamber 14d of the hydraulic cylinder 14 via the second cylinder path 32. The second pump path 34 is connected to the second pump port 12b of the first hydraulic pump 12. The second pump port 13b of the second hydraulic pump 13 is connected to a hydraulic fluid tank 27. Therefore, hydraulic fluid is supplied to the second pump flowpath 34 from the first hydraulic pump 12. The hydraulic fluid flowpath 15 configures a closed circuit between the first hydraulic pump 12 and the hydraulic cylinder 14 with the first pump flowpath 33, the first cylinder flowpath 31, the second cylinder flowpath 32, and the second pump flowpath 34. The hydraulic fluid flowpath 15 configures an open circuit between the second hydraulic pump 13 and the hydraulic cylinder 14 with the first pump flowpath 33 and the first cylinder flowpath 31.
The hydraulic drive system 1 is further provided with a charge circuit 19. The charge circuit 19 has a charge flowpath 35 and a charge pump 28. The charge pump 28 is a hydraulic pump for replenishing the hydraulic fluid flowpath 15 with hydraulic fluid. The charge pump 28 is driven by the engine 11 to discharge hydraulic fluid to the charge flowpath 35. The charge pump 28 is a fixed displacement hydraulic pump. The charge path 35 connects the charge pump 28 with the hydraulic fluid flowpath 15. The charge flowpath 35 is connected between the main pump 10 and a first check valve 44 in the hydraulic fluid flowpath 15. Specifically, the charge path 35 is connected to the first pump flowpath 33 via a check valve 41a. The check valve 41a is open when the hydraulic pressure of the first pump flowpath 33 is lower than the charge pressure of the charge path 35. The charge flowpath 35 is connected between the main pump 10 and a second check valve 45 in the hydraulic fluid flowpath 15. Specifically, the charge path 35 is connected to the second pump flowpath 34 via a check valve 41b. The check valve 41b is open when the hydraulic pressure of the second pump path 34 is lower than the charge pressure. As a result, the charge circuit 19 replenishes the hydraulic fluid flowpath 15 with hydraulic fluid when the hydraulic pressure in the hydraulic fluid flowpath 15 is lower than the charge pressure. The charge flowpath 35 has a first charge flowpath 35a and a second charge flowpath 35b. The first charge flowpath 35a is connected to the charge pump 28. The second charge flowpath 35b is connected to the first charge flowpath 35a via a below mentioned third check valve 49. The second charge flowpath 35b is connected to the first pump path 33 via the abovementioned check valve 41a. The second charge flowpath 35b is connected to the second pump path 34 via the abovementioned check valve 41b. The charge path 35 is connected to the hydraulic fluid tank 27 via a charge relief valve 42. More specifically, the first charge flowpath 35a is connected to the hydraulic fluid tank 27 via the charge relief valve 42. The charge relief valve 42 maintains the charge pressure at a predetermined setting pressure. When the hydraulic pressure of the first pump flowpath 33 or the second pump flowpath 34 becomes lower than the charge pressure, hydraulic fluid from the charge pump 28 is supplied to the first pump flowpath 33 or the second pump flowpath 34 via the charge flowpath 35. As a result, the hydraulic pressures of the first pump flowpath 33 and the second pump flowpath 34 are maintained at a predetermined value or higher.
A discharge pressure reducing unit 39 is connected to the charge flowpath 35. More specifically, the discharge pressure reducing unit 39 is connected to the first charge flowpath 35a. The discharge pressure reducing unit 39 is a so-called bypass valve and is switchable between a connection state Pa and a closed state Pb. The discharge pressure reducing unit 39 connects the first charge flowpath 35a to the hydraulic fluid tank 27 in the connection state Pa. Therefore, the discharge pressure reducing unit 39 reduces the hydraulic pressure in the first charge flowpath 35a in the connection state Pa. Specifically, the discharge pressure reducing unit 39 reduces the discharge pressure of the charge pump 28 in the connection state Pa. The discharge pressure reducing unit 39 closes the connection between the first charge flowpath 35a and the hydraulic fluid tank 27 in the closed state Pb. The discharge pressure reducing unit 39 is a solenoid-operated control valve and is switched between the connection state Pa and the closed state Pb by a command signal from the pump controller 24. Specifically, the discharge pressure reducing unit 39 is set to the closed state Pb due to the biasing force of a biasing member 39a when the command signal from the pump controller 24 indicates OFF. The discharge pressure reducing unit 39 is set to the connection state Pa when the command signal from the pump controller 24 indicates ON.
The hydraulic fluid flowpath 15 further includes a relief flowpath 36. The relief flowpath 36 is connected to the first pump flowpath 33 via a check valve 41c. The check valve 41c is open when the hydraulic pressure of the first pump flowpath 33 is higher than the hydraulic pressure of the relief flowpath 36. The relief flowpath 36 is connected to the second pump flowpath 34 via a check valve 41d. The check valve 41d is open when the hydraulic pressure of the second pump flowpath 34 is higher than the hydraulic pressure of the relief flowpath 36. The relief flowpath 36 is connected to the charge flowpath 35 via a relief valve 43. The relief valve 43 maintains the pressure of the relief flowpath 36 at a pressure equal to or less than a predetermined relief pressure. As a result, the hydraulic pressure of the first pump flowpath 33 and the second pump flowpath 34 is maintained at a pressure equal to or less than the predetermined relief pressure. The hydraulic fluid flowpath 15 further includes an adjustment flowpath 37. The adjustment flowpath 37 is connected to the charge flowpath 35.
An accumulator 38 is connected to the charge flowpath 35. Specifically, the accumulator 38 is connected to the second charge flowpath 35b. The third check valve 49 is connected to the charge flowpath 35. The third check valve 49 is disposed between the first charge flowpath 35a and the second charge flowpath 35b. Specifically, the third check valve 49 is disposed between the accumulator 38 and the charge pump 28. The third check valve 49 allows a flow from the first charge flowpath 35a to the second charge flowpath 35b and prohibits a flow from the second charge flowpath 35b to the first charge flowpath 35a. Specifically, the check valve 39 allows the flow of hydraulic fluid from the charge pump 28 to the accumulator 38 and prohibits the flow of hydraulic fluid from the accumulator 38 to the charge pump 28 in the charge path 35. The third check valve 49 is an example of a one-way valve in the present invention. An accumulated pressure detecting unit 48 is connected to the accumulator 38. The accumulated pressure detecting unit 48 detects an accumulated pressure of the accumulator 38. The accumulated pressure detecting unit 48 sends a detection signal indicating the detected accumulated pressure to the pump controller 24.
The flowpath switching valve 16 is an electromagnetic control valve controlled on the basis of a command signal from the pump controller 24. The flowpath switching valve 16 switches flowpath connections on the basis of a command signal from the pump controller 24. The flowpath switching valve 16 is disposed between the main pump 10 and the hydraulic cylinder 14 in the hydraulic fluid flowpath 15. The flowpath switching valve 16 includes a first pump port 16a, a first cylinder port 16b, a first adjustment port 16c, and a first bypass port 16d. The first pump port 16a is connected to the first pump flowpath 33 via the first check valve 44. The first cylinder port 16b is connected to the first cylinder flowpath 31. The first adjustment port 16c is connected to the adjustment flowpath 37.
The first check valve 44 is disposed between the main pump 10 and the hydraulic cylinder 14 in the hydraulic fluid flowpath 15. The first check valve 44 allows the flow of hydraulic fluid from the main pump 10 to the hydraulic cylinder 14. The first check valve 44 prohibits the flow of hydraulic fluid from the hydraulic cylinder 14 to the main pump 10. Specifically, the first check valve 44 allows the flow of hydraulic fluid from the first pump flowpath 33 to the first cylinder flowpath 31 and prohibits the flow of hydraulic fluid from the first cylinder flowpath 31 to the first pump flowpath 33 when hydraulic fluid is supplied to the first cylinder flowpath 31 from the first pump flowpath 33 by the flowpath switching valve 16.
The flowpath switching valve 16 further includes a second pump port 16e, a second cylinder port 16f, a second adjustment port 16g, and a second bypass port 16h. The second pump port 16e is connected to the second pump flowpath 34 via a second check valve 45. The second check valve 45 is a check valve for restricting the flow of hydraulic fluid to one direction. The second cylinder port 16f is connected to the second cylinder flowpath 32. The second adjustment port 16g is connected to the adjustment flowpath 37.
The second check valve 45 is disposed between the main pump 10 and the hydraulic cylinder 14 in the hydraulic fluid flowpath 15. The second check valve 45 allows the flow of hydraulic fluid from the main pump 10 to the hydraulic cylinder 14. The second check valve 45 prohibits the flow of hydraulic fluid from the hydraulic cylinder 14 to the main pump 10. Specifically, the second check valve 45 allows the flow of hydraulic fluid from the second pump flowpath 34 to the second cylinder flowpath 32 and prohibits the flow of hydraulic fluid from the second cylinder flowpath 32 to the second pump flowpath 34 when hydraulic fluid is supplied to the second cylinder flowpath 32 from the second pump flowpath 34 by the flowpath switching valve 16.
The flowpath switching valve 16 is switchable between a first position state P1, a second position state P2, and a neutral position state Pn. The flowpath switching valve 16 allows communication between the first pump port 16a and the first cylinder port 16b and between the second cylinder port 16f and the second bypass port 16h in the first position state P1. Therefore, the flowpath switching valve 16 connects the first pump flowpath 33 to the first cylinder flowpath 34 via the first check valve 44 and connects the second cylinder flowpath 32 to the second pump flowpath 34 without passing through the second check valve 45 in the first position state P1. The first bypass port 16d, the first adjustment port 16c, the second pump port 16e, and the second adjustment port 16g are all cut off from communication with any port when the flowpath switching valve 16 is in the first position state P1.
When the hydraulic cylinder 14 is expanded, the first hydraulic pump 12 and the second hydraulic pump 13 are driven in the first discharge state and the flowpath switching valve 16 is set to the first position state P1. As a result, hydraulic fluid discharged from the first pump port 12a of the first hydraulic pump 12 and from the first pump port 13a of the second hydraulic pump 13 passes through the first pump path 33, the first check valve 44, and the first cylinder path 31 to be supplied to the first chamber 14c of the hydraulic cylinder 14. The hydraulic fluid in the second chamber 14d of the hydraulic cylinder 14 passes through the second cylinder path 32 and the second pump path 34 and is recovered in the second pump port 12b of the first hydraulic pump 12. As a result, the hydraulic cylinder 14 expands.
The flowpath switching valve 16 allows communication between the second pump port 16e and the second cylinder port 16f and between the first cylinder port 16b and the first bypass port 16d in the second position state P2. Therefore, the flowpath switching valve 16 connects the first cylinder flowpath 31 to the first pump flowpath 33 without passing through the first check valve 44 and connects the second pump flowpath 34 to the second cylinder flowpath 32 via the second check valve 45 in the second position state P2. The first pump port 16a, the first adjustment port 16c, the second bypass port 16h, and the second adjustment port 16g are all cut off from communication with any port when the flowpath switching valve 16 is in the second position state P2.
When the hydraulic cylinder 14 is contracted, the first hydraulic pump 12 and the second hydraulic pump 13 are driven in a second discharge state and the flowpath switching valve 16 is set to the second position state P2. As a result, hydraulic fluid discharged from the second pump port 12b of the first hydraulic pump 12 passes through the second pump flowpath 34, the second check valve 45, and the second cylinder flowpath 32 to be supplied to the second chamber 14d of the hydraulic cylinder 14. The hydraulic fluid in the first chamber 14c of the hydraulic cylinder 14 passes through the first cylinder path 31a and the first pump path 33 to be recovered in the first pump port 12a of the first hydraulic pump 12 and in the first pump port 13a of the second hydraulic pump 13. As a result, the hydraulic cylinder 14 contracts.
The flowpath switching valve 16 allows communication between the first bypass port 16d and the first adjustment port 16c, and between the second bypass port 16h and the second adjustment port 16g in the neutral position state Pn. Therefore, the flowpath switching valve 16 connects the first pump flowpath 33 to the adjustment flowpath 37 without passing through the first check valve 44, and connects the second pump flowpath 34 to the adjustment flowpath 37 without passing through the second check valve 45 in the neutral position state Pn. When the flowpath switching valve 16 is in the neutral position state Pn, the first pump port 16a, the first cylinder port 16b, the second pump port 16e, and the second cylinder port 16f are all cut off from communication with any port.
The hydraulic drive system 1 further includes an operating device 46. The operating device 46 includes an operating member 46a and an operation detecting unit 46b. The operating member 46a is operated by an operator to command various types of operations of the work machine. For example, when the hydraulic cylinder 14 is a boom cylinder for driving a boom, the operating member 46a is a boom operating lever for operating the boom. The operating member 46a may be operated in two directions: a direction for expanding the hydraulic cylinder 14 from the neutral position, and a direction for contracting the hydraulic cylinder 14 from the neutral position. The operation detecting unit 46b detects the operation amount and the operation direction of the operating member 46a. The operation detecting unit 46b is a sensor for detecting a position of the operating member 46a, for example. When the operating member 46a is positioned in the neutral position, the operation amount of the operating member 46a is zero. Detection signals that indicate the operation amount and the operation direction of the operating member 46a are input from the operation detecting unit 46b to the pump controller 24. The pump controller 24 calculates a target flow rate of the hydraulic fluid to be supplied to the hydraulic cylinder 14 in response to the operation amount of the operating member 46a.
The hydraulic drive system 1 further includes a display device 47. The display device 47 is, for example, a liquid crystal monitor display device. The display device 47 displays various types of information pertaining to the work machine in response to a command signal from the pump controller 24.
The engine controller 22 controls the output of the engine 11 by controlling the fuel injection device 21. Engine output torque characteristics determined on the basis of a set target engine rotation speed and a work mode are mapped and stored in the engine controller 22. The engine output torque characteristics indicate the relationship between the output torque and the rotation speed of the engine 11. The engine controller 22 controls the output of the engine 11 on the basis of the engine output torque characteristics.
The pump controller 24 controls the flow rate of hydraulic fluid to be supplied to the hydraulic cylinder 14 in response to the target flow rate set by the operating member 46a. When the hydraulic cylinder 14 is expanded, the pump controller 24 uses the first pump-flow-rate control unit 25 and the second pump-flow-rate control unit 26 to control the flow rate of hydraulic fluid to be supplied to the hydraulic cylinder 14. When the hydraulic cylinder 14 is contracted, the pump controller 24 uses the first pump-flow-rate control unit 25 to control the flow rate of the hydraulic fluid being supplied to the hydraulic cylinder 14.
The pump controller 24 controls the flowpath switching valve 16 in accordance with the operating direction of the operating member 46a. When the operating member 46a is operated in the direction for expanding the hydraulic cylinder 14 from the neutral position, the pump controller 24 sets the flowpath switching valve 16 to the first position state P1. As a result, the first pump flowpath 33 and the first cylinder flowpath 31 are connected via the first check valve 44. Furthermore, the second pump flowpath 34 and the second cylinder flowpath 32 are connected without passing through the second check valve 45. The hydraulic fluid is then discharged from the first pump port 12a of the first hydraulic pump 12 and from the first pump port 13a of the second hydraulic pump 13 to the first pump flowpath 33. However, the first check valve 44 does not open until the hydraulic pressure in the first pump flowpath 33 exceeds the holding pressure in the first cylinder flowpath 31 and the hydraulic cylinder 14 does not operate. Conversely, hydraulic fluid in the second pump path 34 is sucked into the second pump port 12b of the first hydraulic pump 12. As a result, the hydraulic pressure in the second pump flowpath 34 decreases. When the hydraulic pressure in the second pump flowpath 34 becomes equal to or less than the charge pressure, the check valve 41b opens to allow communication between the charge flowpath 35 and the second pump flowpath 34. As a result, the second pump flowpath 34 is replenished with hydraulic fluid from the charge flowpath 35. At this time, the second pump flowpath 34 is replenished, via the charge flowpath 35, with hydraulic fluid from the charge pump 28 and with hydraulic fluid from the accumulator 38 that was stored beforehand by the charge pump 28. When the hydraulic pressure in the first pump flowpath 33 exceeds the holding pressure of the first cylinder flowpath 31, the first check valve 44 opens and allows communication between the first pump flowpath 33 and the first cylinder flowpath 31. As a result, hydraulic fluid is supplied to the first chamber 14c of the hydraulic cylinder 14 and the hydraulic cylinder 14 expands. While the hydraulic cylinder 14 is expanding, hydraulic fluid is exhausted from the second chamber 14d of the hydraulic cylinder 14, passes through the second cylinder path 32 and the second pump path 34, and is returned to the second pump port 12b of the first hydraulic pump 12. At this time, the second pump flowpath 34 is replenished, from the charge flowpath 35, with hydraulic fluid at a flow rate required for compressing the hydraulic fluid in the first hydraulic pump 12, and hydraulic fluid at a flow rate sufficient to allow a leakage amount of hydraulic fluid in the first hydraulic pump 12 to be replenished.
When the operating member 46a is operated in the direction for contracting the hydraulic cylinder 14 from the neutral position, the pump controller 24 sets the flowpath switching valve 16 to the second position state P2. As a result, the second pump flowpath 34 and the second cylinder flowpath 32 are connected via the second check valve 45. Further, the first pump flowpath 33 and the first cylinder flowpath 31 are connected without passing through the first check valve 44. The hydraulic fluid is then discharged from the second pump port 12b of the first hydraulic pump 12 to the second pump flowpath 34. However, the second check valve 45 does not open until the hydraulic pressure in the second pump flowpath 34 exceeds the holding pressure in the second cylinder flowpath 32, and thus the hydraulic cylinder 14 does not operate. Conversely, hydraulic fluid in the first pump flowpath 33 is sucked into the first pump port 12 of the first hydraulic pump 12 and into the first pump port 13a of the second hydraulic pump 13. As a result, the hydraulic pressure in the first pump flowpath 33 decreases. When the hydraulic pressure in the first pump flowpath 33 becomes equal to or less than the charge pressure, the check valve 41a opens to allow communication between the charge flowpath 35 and the first pump flowpath 33. As a result, the first pump flowpath 33 is replenished with hydraulic fluid from the charge flowpath 35. At this time, the first pump flowpath 33 is replenished, via the charge flowpath 35, with hydraulic fluid from the charge pump 28 and with hydraulic fluid from the accumulator 38 that was stored beforehand by the charge pump 28. When the hydraulic pressure in the second pump flowpath 34 exceeds the holding pressure in the second cylinder flowpath 32, the second check valve 45 opens to allow communication between the second pump flowpath 34 and the second cylinder flowpath 32. As a result, hydraulic fluid is supplied to the second chamber 14d of the hydraulic cylinder 14, and thus the hydraulic cylinder 14 contracts. The hydraulic fluid is exhausted during a contraction of the hydraulic cylinder 14 from the first chamber 14c of the hydraulic cylinder 14, passes through the first cylinder path 31a and the first pump path 33, and is returned to the first pump port 12a of the first hydraulic pump 12 and to the first pump port 13a of the second hydraulic pump 13. At this time, the first pump flowpath 33 is replenished, from the charge flowpath 35, with hydraulic fluid at a flow rate required for compressing the hydraulic fluid in the first hydraulic pump 12, and hydraulic fluid at a flow rate sufficient to allow a leakage amount of hydraulic fluid in the first hydraulic pump 12 to be replenished.
Next, control of the discharge pressure of the charge pump 28 executed by the pump controller 24 will be described. The pump controller 24 has a pump control unit 24a, a memory unit 24b, an operating state determining unit 24c, a discharge pressure control unit 24d, and an accumulated pressure determining unit 24e. The pump control unit 24a, the operating state determining unit 24c, the discharge pressure control unit 24d, and the accumulated pressure determining unit 24e may be realized by a calculation device, such as a CPU and the like. The memory unit 24b may be realized by a recording device, such as a RAM, a ROM, a hard disk, or a flash memory and the like. The pump control unit 24a controls the discharge flow rate of the main pump 10 on the basis of an operating position of the operating member 46a. Specifically, the pump controller 24 calculates a target flow rate of the hydraulic fluid to be supplied to the hydraulic cylinder 14 in response to the operation amount of the operating member 46a. The memory unit 24b stores information for controlling the first hydraulic pump 12 and the second hydraulic pump 13.
In step S101, the operation detecting unit 46b detects the operating position of the operating member 46a. In step S102, the operating state determining unit 24c determines whether the operating position is the neutral position. The routine advances to step S103 when the operating position is the neutral position. In step S103, the operating state determining unit 24c detects an elapsed time t. The elapsed time t is a time period from the point in time that the operating member 46a is switched to the neutral position to the current time. In step S104, the operating state determining unit 24c determines whether the elapsed time t is equal to or greater than a predetermined time to. The routine advances to step S105 when the elapsed time t is equal to or greater than the predetermined time t0. In this way, the operating state determining unit 24c determines in steps S101 to S104 whether the hydraulic cylinder 14 is in an operating state or a non-operating state on the basis of the detection signal from the operation detecting unit 46b. Specifically, the operating state determining unit 24c determines that the hydraulic cylinder 14 is in the non-operating state when the operating member 46a is held in the neutral position for a time period equal to or greater than the predetermined time t0. The operating state determining unit 24c determines that the hydraulic cylinder 14 is in operation when the holding time of the operating member 46a in the neutral position is less than the predetermined time t0. The operating state determining unit 24c determines that the hydraulic cylinder 14 is in operation when the operating member 46a is in a position other than the neutral position.
In step S105, the discharge pressure control unit 24d sets the discharge pressure reducing unit 39 to the connection state Pa. Specifically, the discharge pressure control unit 24d switches the discharge pressure reducing unit 39 from the closed state Pb to the connection state Pa by sending a command signal that indicates ON to the discharge pressure reducing unit 39. As a result, the discharge pressure of the charge pump 28 is reduced to a low pressure lower than the normal pressure.
In step S102, the routine returns to step S101 when the operating position is not the neutral position. In step S104, the routine returns to step S103 when the elapsed time t is less than the predetermined time t0. Specifically, when the operating state determining unit 24c determines that the hydraulic cylinder 14 is in operation, the discharge pressure control unit 24d maintains the discharge pressure reducing unit 39 in the closed state Pb. As a result, the discharge pressure of the charge pump 28 is maintained at the normal pressure while the hydraulic cylinder 14 is in operation.
In step S106, the accumulated pressure detecting unit 48 detects an accumulated pressure Pacc in the accumulator 38. In step S107, the accumulated pressure determining unit 24e determines whether the accumulated pressure Pacc is equal to or less than a first setting pressure. The first setting pressure corresponds to a lower limit of the accumulated pressure required in the accumulator 38. The routine advances to step S108 when the accumulated pressure Pacc is equal to or less than the first setting pressure.
In step S108, the discharge pressure control unit 24d sets the discharge pressure reducing unit 39 to the closed state Pb. As a result, hydraulic fluid to be discharged by the charge pump 28 is stored in the accumulator 38. Consequently, the discharge pressure of the charge pump 28 recovers from the low pressure to the normal pressure.
In step S109, the accumulated pressure determining unit 24e determines whether the accumulated pressure Pacc is equal to or greater than a second setting pressure. The second setting pressure is higher than the first setting pressure. The routine advances to step S109 when the accumulated pressure Pacc is equal to or greater than the second setting pressure.
In step S110, the discharge pressure control unit 24d sets the discharge pressure reducing unit 39 to the connection state Pa. As a result, the discharge pressure of the charge pump 28 is changed from the normal pressure to low pressure. Specifically, the discharge pressure control unit 24d returns the discharge pressure of the charge pump 28 from the normal pressure to the low pressure when the accumulated pressure of the accumulator 38 recovers from a pressure equal to or less than the first setting pressure to a pressure equal to or greater than the second setting pressure while the hydraulic cylinder 14 is not in operation.
When the accumulated pressure Pacc is not equal to or greater than the second setting pressure in step S109, the routine returns to step S108. As a result, the discharge pressure of the charge pump 28 is maintained at the normal pressure. Specifically, the discharge pressure control unit 24d maintains the discharge pressure of the charge pump 28 at the normal pressure until the accumulated pressure of the accumulator 38 recovers from a pressure equal to or less than the first setting pressure to a pressure equal to or greater than the second setting pressure.
In step S202, the accumulated pressure detecting unit 48 detects the accumulated pressure Pacc in the accumulator 38. In step S203, the accumulated pressure determining unit 24e determines whether the accumulated pressure Pacc is greater than a third setting pressure. The third setting pressure is equal to or higher than the first setting pressure. The third setting pressure may be the same as the first setting pressure. The routine advances to step S204 if the accumulated pressure Pacc is greater than the third setting pressure.
In step S204, the pump control unit 24a starts the discharge from the main pump 10. Specifically, the pump control unit 24a increases the displacements of the first hydraulic pump 12 and the second hydraulic pump 13 by controlling the first pump-flow-rate control unit 25 and the second pump-flow-rate control unit 26.
When the accumulated pressure Pacc is equal to or less than the third setting pressure in step S203, the pump control unit 24a causes the display device 47 to display a standby display in step S205. The standby display indicates that the standby control is being executed. Specifically, the standby display is used for notifying an operator that the discharge of the main pump 10 has not started due to the execution of the standby control.
As illustrated in steps S203 to S205, the pump control unit 24a does not start the discharge of hydraulic fluid from the main pump 10 until the accumulated pressure in the accumulator 38 is greater than the third setting pressure even if an activation operation is conducted by the operating member 46a when the accumulated pressure in the accumulator 38 is equal to or less than the third setting pressure.
The hydraulic drive system 1 according to the present exemplary embodiment has the following features.
The abovementioned control of the discharge pressure of the charge pump 28 allows for the reduction of the discharge pressure of the charge pump 28 to a low pressure when the hydraulic cylinder 14 is not in operation. As a result, power consumption loss of the charge pump 28 may be reduced. Moreover, when the pressure in the hydraulic fluid flowpath 15 between the main pump 10 and the check valves 44 and 45 is raised up to the holding pressure, the hydraulic fluid flowpath 15 may be replenished with hydraulic fluid discharged from the charge pump 28 and hydraulic fluid stored in the accumulator 38. As a result, the charge pump 28 may be made smaller in comparison to when the hydraulic fluid flowpath 15 is replenished with hydraulic fluid only from the charge pump 28. As a result, power consumption loss of the charge pump 28 may be reduced.
When the charge pump 28 is stopped, the flow of the hydraulic fluid stored in the accumulator 38 to the charge pump 28 is prohibited due to the third check valve 49. As a result, a reduction in the accumulated pressure of the accumulator may be suppressed.
The discharge pressure control unit 24d changes the discharge pressure of the charge pump 28 from low pressure to the normal pressure when the accumulated pressure of the accumulator 38 becomes equal to or less than the first setting pressure while the hydraulic cylinder 14 is not in operation. As a result, a reduction in the accumulated pressure of the accumulator may be suppressed even when the hydraulic cylinder 14 is maintained in a non-operating state for a long period of time. Specifically, the occurrence of aeration or of cavitation in the first hydraulic pump 12 may be suppressed when operation of the hydraulic cylinder is started.
The discharge pressure of the charge pump 28 is returned from the normal pressure to the low pressure when the accumulated pressure of the accumulator 38 recovers to be equal to or greater than the second setting pressure. As a result, power consumption loss of the charge pump 28 may be reduced.
The discharge of hydraulic fluid from the main pump 10 is not started until the accumulated pressure of the accumulator 38 exceeds the third setting pressure even when the activation operation is conducted by the operating member 46a. As a result, the occurrence of aeration or of cavitation in the first hydraulic pump 12 may be suppressed. The third setting pressure is equal to or higher than the first setting pressure. The discharge of hydraulic fluid from the main pump 10 may be started in a state in which a required amount of hydraulic fluid is stored in the accumulator 38.
The standby display is displayed on the display device 47 when the discharge of hydraulic fluid from the main pump 10 is stopped due to the standby control. As a result, the operator may be notified that the main pump 10 is not activated because the standby control is being executed.
The operating state determining unit 24c determines that the hydraulic cylinder 14 is in the non-operating state when the operating member 46a is held in the neutral position for a time equal to or greater than the predetermined time t0 during the discharge pressure control of the charge pump 28. As a result, the mistaken determination that the hydraulic cylinder 14 is not in operation when the hydraulic cylinder 14 is actually in operation when the operating member 46a temporarily passes through the neutral position, may be prevented.
Switching the direction of the flow of the hydraulic fluid to the hydraulic cylinder 14 is not limited to being conducted by the flowpath switching valve 16 of the first exemplary embodiment, and the switching may be conducted with another configuration.
When the operating member 46a is operated in the direction for expanding the hydraulic cylinder 14 from the neutral position, the pump controller 24 sets the first pilot check valve 51 to the restricted state and sets the second pilot check valve 52 to the open state. Therefore, if the hydraulic pressure in the first pump flowpath 33 exceeds the holding pressure in the first cylinder flowpath 31, the first pilot check valve 51 is opened and hydraulic fluid discharged from the first hydraulic pump 12 and from the second hydraulic pump 13 passes through the first pump flowpath 33 and the first cylinder flowpath 31 to be supplied to the first chamber 14c of the hydraulic cylinder 14. Hydraulic fluid is exhausted from the second chamber 14d of the hydraulic cylinder 14, passes through the second cylinder flowpath 32 and the second pump flowpath 34, and is returned to the first hydraulic pump 12.
When the operating member 46a is operated in the direction to contract the hydraulic cylinder 14 from the neutral position, the pump controller 24 sets the first pilot check valve 51 to the open state and sets the second pilot check valve 52 to the restricted state. Therefore, if the hydraulic pressure in the second pump flowpath 34 exceeds the holding pressure in the second cylinder flowpath 32, hydraulic fluid discharged from the first hydraulic pump 12 passes through the second pump flowpath 34 and the second cylinder flowpath 32 to be supplied to the second chamber 14d of the hydraulic cylinder 14. Hydraulic fluid is exhausted from the first chamber 14c of the hydraulic cylinder 14, passes through the first cylinder flowpath 31 and the first pump flowpath 33, and is returned to the first hydraulic pump 12 and to the second hydraulic pump 13.
Other control functions and configurations of the hydraulic drive system 2 are the same as those of the hydraulic drive system 1 in the first exemplary embodiment. The hydraulic drive system 2 of the second exemplary embodiment has the same features as the hydraulic drive system 1 of the first exemplary embodiment.
Although exemplary embodiments of the present invention have been described, the present invention is not limited to the above exemplary embodiments and various modifications may be made within the scope of the invention.
The pump-flow-rate control units 25 and 26 in the above first exemplary embodiment and second exemplary embodiment control the discharge flow rate of the hydraulic pumps 12 and 13 by controlling the tilt angles of the hydraulic pumps 12 and 13. However, the discharge flow rates of the hydraulic pumps 12 and 13 may be controlled by controlling the rotation speeds of the hydraulic pumps 12 and 13. For example, an electric motor 57 may be used as a driving source as illustrated in
In the above exemplary embodiments, the discharge pressure reducing unit 39 is set to the closed state Pb when the command signal from the pump controller 24 indicates OFF. The discharge pressure reducing unit 39 is set to the connection state Pa when the command signal from the pump controller 24 indicates ON. However, in contrast to the above explanation, the discharge pressure reducing unit 39 may be set to the connection state Pa due to the biasing force of a biasing member 39a when the command signal from the pump controller 24 indicates OFF. The discharge pressure reducing unit 39 may be set to the closed state Pb by a solenoid thrust force when the command signal from the pump controller 24 indicates ON.
The discharge pressure reducing unit is not limited to a bypass valve and may be a device that enable to reduce the discharge pressure of the charge pump 28 to a pressure lower than a setting pressure of the charge relief valve 42. For example, the charge relief valve 42 may be used as a discharge pressure reducing unit. In this case, the relief pressure of the charge relief valve 42 is switched between a first relief pressure and a second relief pressure. The first relief pressure corresponds to the abovementioned normal pressure. The second relief pressure corresponds to the abovementioned low pressure. The charge relief valve 42 reduces the discharge pressure of the charge pump 28 by switching the relief pressure from the first relief pressure to the second relief pressure on the basis of a command signal from the pump controller 24.
A one-way valve other than a check valve may be used in place of the third check valve 49. The display device 47 is not limited to a screen device and another display device, such as a warning light, may be used. The determination of whether the hydraulic cylinder 14 is in operation or is not in operation is not limited to the operation of the operating member 46a and another method may be used for the determination. For example, the determination of whether the hydraulic cylinder 14 is in operation or is not in operation may be conducted by detecting the operation of the hydraulic cylinder 14. However, the operating state determining unit 24c preferably conducts the determination on the basis of the operation of the operating member 46a due to the execution of the abovementioned standby control.
According to the present invention, a hydraulic drive system that is able to reduce power consumption loss in the charge pump may be provided.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2012-039787 | Feb 2012 | JP | national |
This application is a U.S. National stage application of International Application No. PCT/JP2012/073119, filed on Sep. 11, 2012. This U.S. National stage application claims priority under 35 U.S.C. §119(a) to Japanese Patent Application No. 2012-039787, filed in Japan on Feb. 27, 2012, the entire contents of which are hereby incorporated herein by reference.
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2012/073119 | 9/11/2012 | WO | 00 | 8/11/2014 |
