Patent Application
20250188710
The present invention relates to a hydraulic drive apparatus that supplies a working fluid to a travel motor and a loading actuator.
A one-pump system in which a single pump serves as hydraulic sources for a travel motor and a loading actuator of construction equipment has been put into practice. For example, a hydraulic circuit such as that disclosed in Patent Literature (PTL) 1 is known as a hydraulic drive apparatus for the one-pump system. In the hydraulic circuit disclosed in PTL 1, a pump is connected to a travel motor and a loading actuator via a first pump line and a second pump line. Furthermore, a priority valve is provided on the second pump line. A supply pressure for the travel motor acts on the priority valve. Therefore, with the priority valve, when the supply pressure for the travel motor increases, pressure oil preferentially flows to the travel motor.
PTL 1: Japanese Laid-Open Patent Application Publication No. 2020-026828
In the hydraulic circuit disclosed in PTL 1, the priority valve restricts the opening degree of the second pump line according to the supply pressure that acts thereon. Therefore, in the priority valve, the relationship between the supply pressure and the opening degree of the second pump line is determined on a one-to-one basis. Thus, the degree of freedom for the priority valve is low regarding the control of the opening degree of the second pump line.
In view of this, an object of the present invention is to provide a hydraulic drive apparatus capable of improving the degree of freedom of control regarding the opening degree of a passage leading to a loading actuator.
A hydraulic drive apparatus according to the present invention supplies a working fluid to each of a travel motor and a loading actuator and includes: a hydraulic pump that discharges the working fluid; a flow dividing valve that divides, as a first passage and a second passage, a pump passage connected to the hydraulic pump, and changes an opening degree of each of the first passage and the second passage according to an opening degree signal that is input to the flow dividing valve; a travel system hydraulic circuit that is connected to the first passage and controls a flow of the working fluid to the travel motor; a loading system hydraulic circuit that is connected to the second passage and controls a flow of the working fluid to the loading actuator; a travel-end pressure sensor that detects a travel-end supply pressure that is a pressure being supplied to the travel motor; and a control device that controls, by outputting the opening degree signal to the flow dividing valve, the opening degree of the first passage and the opening degree of the second passage according to the travel-end supply pressure detected by the travel-end pressure sensor.
According to the present invention, the control device controls the opening degree of the first passage and the opening degree of the second passage according to the travel-end supply pressure by outputting the opening degree signal to the flow dividing valve. Therefore, by changing the control logic of the control device, it is possible to easily adjust the opening degrees of the first passage and the second passage that are opened in relation to the travel-end supply pressure. Thus, it is possible to improve the degree of freedom of control regarding the opening degree of the second passage leading to the loading actuator.
According to the present invention, it is possible to improve the degree of freedom of control regarding the opening degree of a passage leading to a loading actuator.
The above object, other objects, features, and advantages of the present invention will be made clear by the following detailed explanation of preferred embodiments with reference to the attached drawings.
Hereinafter, hydraulic drive apparatuses 1, 1A, 1B according to Embodiments 1 to 3 of the present invention will be described with reference to the aforementioned drawings. Note that the concept of directions mentioned in the following description is used for the sake of explanation; the orientations, etc., of elements according to the invention are not limited to these directions. Each of the hydraulic drive apparatuses 1, 1A, 1B described below is merely one embodiment of the present invention. Thus, the present invention is not limited to the embodiments and may be subject to addition, deletion, and alteration within the scope of the essence of the invention.
The hydraulic drive apparatus 1 illustrated in
The vehicle body, which is a tracked vehicle, for example, includes a pair of left and right crawlers (not illustrated in the drawings) and a pair of left and right travel motors 2, 3, for example. The vehicle body travels by actuating the pair of left and right crawlers. Note that the vehicle body may be a wheeled device; it is sufficient that the vehicle body be a device capable of traveling. The travel motors 2, 3, which are hydraulic motors, drive the left and right crawlers, respectively. More specifically, the travel motor 2 includes two supply/drainage ports 2a, 2b, and the travel motor 3 includes two supply/drainage ports 3a, 3b. The travel motors 2, 3 rotate in a normal direction when the working fluid is supplied to one of the supply/drainage ports, namely, the supply/drainage ports 2a, 3a, and rotate in the reverse direction when the working fluid is supplied to the other of the supply/drainage ports, namely, the supply/drainage ports 2b, 3b.
The work equipment includes a boom, an arm, a bucket (all of which are not illustrated in the drawings), and a plurality of loading actuators 4 to 6. The work equipment is rotatably provided on the vehicle body. In the present embodiment, the loading actuators 4 to 6 are hydraulic cylinders 4 to 6. The hydraulic cylinders 4 to 6 are provided on the boom, the arm, and the bucket, respectively. The work equipment moves the boom, the arm, and the bucket by extending and retracting the three hydraulic cylinders 4 to 6. Thus, the work equipment can perform various tasks.
The hydraulic drive apparatus 1 includes a hydraulic pump 11, a flow dividing valve 12, a travel system hydraulic circuit 13, a loading system hydraulic circuit 14, travel-end pressure sensors 15, 16, and a control device 17. More specifically, the hydraulic drive apparatus 1 further includes loading-end pressure sensors 18 to 20, a travel system operation device 21, and a loading system operation device 22. The hydraulic drive apparatus 1, which is a so-called one-pump system, supplies the working fluid from one hydraulic pump 11 to the travel motors 2, 3 and the three third hydraulic cylinders 4 to 6. By supplying the working fluid to the first travel motor 2 and the second travel motor 3, the hydraulic drive apparatus 1 actuates the crawlers corresponding, respectively, to the travel motors 2, 3. Thus, the hydraulic drive apparatus 1 can cause the hydraulic excavator to travel. By supplying the working fluid to the hydraulic cylinders 4 to 6, the hydraulic drive apparatus 1 actuates the corresponding boom, arm, and bucket. Thus, the hydraulic drive apparatus 1 can cause the hydraulic excavator to perform various tasks.
The hydraulic pump 11 discharges the working fluid. More specifically, the hydraulic pump 11 is connected to a drive source not illustrated in the drawings (for example, an engine and an electric motor). The hydraulic pump 11 is connected to a pump passage 25. The hydraulic pump 11 is rotatably driven by the drive source and thereby discharges the working fluid to the pump passage 25.
The flow dividing valve 12 is an electrically controlled valve. The flow dividing valve 12, which is an electrically controlled spool valve, for example, includes a flow dividing spool 12a. The flow dividing valve 12 divides the pump passage 25 as a first passage 26 and a second passage 27. In other words, the flow dividing valve 12 divides the working fluid discharged from the hydraulic pump 11. The flow dividing valve 12 changes the opening degree of each of the first passage 26 and the second passage 27 according to an input opening degree signal. Accordingly, the flow dividing valve 12 changes the flow rate of the working fluid that flows to each of the first passage 26 and the second passage 27 according to the input opening degree signal. In the present embodiment, one flow dividing valve 12 is provided for one hydraulic pump 11 in the hydraulic drive apparatus 1. In the hydraulic drive apparatus 1, one flow dividing valve 12 can change the flow rate of the working fluid that flows to each of the first passage 26 and the second passage 27.
The flow dividing spool 12a can move to a first position A1 and a second position A2 according to the input opening degree signal. The flow dividing valve 12 includes a proportional solenoid valve 12b and a spring 12c. The proportional solenoid valve 12b outputs, to the flow dividing spool 12a, a pilot pressure corresponding to the opening degree signal. The spring 12c acts on the flow dividing spool 12a against the pilot pressure of the proportional solenoid valve 12b. Therefore, the flow dividing spool 12a moves to the first position A1 and the second position A2 according to the pilot pressure that is output from the proportional solenoid valve 12b.
The flow dividing spool 12a at the first position A1 restricts the opening degree of the first passage 26, and the flow dividing spool 12a at the second position A2 restricts the opening degree of the second passage 27. More specifically, the flow dividing spool 12a at the first position A1 restricts the opening degree of the first passage 26 and opens the second passage 27. On the other hand, the flow dividing spool 12a at the second position A2 restricts the opening degree of the second passage 27 and opens the first passage 26. In the state where no pilot pressure is output, the flow dividing spool 12a is held at the first position A1 by the spring 12c. When the pilot pressure is output, the flow dividing spool 12a moves to the second position A2.
The flow dividing spool 12a moves with a stroke length corresponding to the opening degree signal. At the first position A1 and the second position A2, the flow dividing spool 12a changes the opening degrees of the passages 26, 27 according to stroke lengths. More specifically, the flow dividing spool 12a increases the opening degree of the first passage 26 as the flow dividing spool 12a moves from the first position A1 to the second position A2, and increases the opening degree of the second passage 27 as the flow dividing spool 12a moves from the second position A2 to the first position A1.
The travel system hydraulic circuit 13 includes a first traveling directional control valve 31 and a second traveling directional control valve 32. The travel system hydraulic circuit 13 is connected to the first passage 26, the first travel motor 2, and the second travel motor 3. The travel system hydraulic circuit 13 supplies the working fluid to each of the first travel motor 2 and the second travel motor 3. The travel system hydraulic circuit 13 controls the flow of the working fluid to each of the first travel motor 2 and the second travel motor 3. More specifically, the travel system hydraulic circuit 13 supplies, to the first travel motor 2 and the second travel motor 3, the working fluid that flows (in the present embodiment, at a flow rate in a flow direction) according to the input first travel command and the input second travel command.
The first traveling directional control valve 31 includes a first traveling spool 31a. The first traveling directional control valve 31 controls the flow of the working fluid to the first travel motor 2. More specifically, the first traveling directional control valve 31 is connected to the first passage 26, a tank 28, and the two supply/drainage ports 2a, 2b of the first travel motor 2. The first traveling spool 31a moves according to the input first travel command. As a result, destinations to which the supply/drainage ports 2a, 2b are connected are switched to the first passage 26 and the tank 28. The first traveling spool 31a changes the opening degree according to the position thereof. Therefore, the working fluid is supplied from the first traveling directional control valve 31 to the first travel motor 2 at a flow rate corresponding to the first travel command, in a direction corresponding to the first travel command. Thus, the first traveling directional control valve 31 causes the first travel motor 2 to rotate in normal and reverse directions according to the first travel command, and causes the first travel motor 2 to rotate at a speed corresponding to the first travel command. In the present embodiment, the first traveling directional control valve 31 is an electrically controlled directional control valve.
The second traveling directional control valve 32 includes a second traveling spool 32a. The second traveling directional control valve 32 controls the flow of the working fluid to the second travel motor 3. More specifically, the second traveling directional control valve 32 is connected to the first passage 26 so as to be parallel to the first traveling directional control valve 31. Furthermore, the second traveling directional control valve 32 is connected to the tank 28 and the two supply/drainage ports 3a, 3b of the second travel motor 3. The second traveling spool 32a moves according to the input second travel command. As a result, destinations to which the supply/drainage ports 3a, 3b are connected are switched to the first passage 26 and the tank 28. The second traveling spool 32a changes the opening degree according to the position thereof. Therefore, the working fluid is supplied from the second traveling directional control valve 32 to the second travel motor 3 at a flow rate corresponding to the second travel command, in a direction corresponding to the second travel command. Thus, the second traveling directional control valve 32 causes the second travel motor 3 to rotate in normal and reverse directions according to the second travel command, and causes the second travel motor 3 to rotate at a speed corresponding to the second travel command. In the present embodiment, the second traveling directional control valve 32 is an electrically controlled directional control valve.
The loading system hydraulic circuit 14 includes a plurality of loading directional control valves 41 to 43. In the present embodiment, the loading system hydraulic circuit 14 includes three loading directional control valves 41 to 43. The three loading directional control valves 41 to 43 are a boom directional control valve 41, an arm directional control valve 42, and a bucket directional control valve 43. The loading system hydraulic circuit 14 is connected to the second passage 27 and the three hydraulic cylinders 4 to 6. The loading system hydraulic circuit 14 supplies the working fluid to each of the three hydraulic cylinders 4 to 6. The loading system hydraulic circuit 14 controls the flow of the working fluid to each of the hydraulic cylinders 4 to 6. More specifically, the loading system hydraulic circuit 14 supplies, to the three hydraulic cylinders 4 to 6, the working fluid that flows (in the present embodiment, at a flow rate in a flow direction) according to the input loading command.
The three loading directional control valves 41 to 43 include loading spools 41a to 43a, respectively. The three loading directional control valves 41 to 43 control the flow of the working fluid to the corresponding hydraulic cylinders 4 to 6. Specifically, the boom directional control valve 41 controls the flow of the working fluid to the boom cylinder 4. The arm directional control valve 42 controls the flow of the working fluid to the arm cylinder 5. The bucket directional control valve 43 controls the flow of the working fluid to the bucket cylinder 6. The three loading directional control valves 41 to 43 are connected to the second passage 27 so as to be parallel to each other. Furthermore, the three loading directional control valves 41 to 43 are connected to the tank 28 and rod-end ports 4a, 5a, 6a and head-end ports 4b, 5b, 6b of the hydraulic cylinders 4 to 6. The loading spools 41a to 43a move according to a boom command, an arm command, and a bucket command. Thus, directions to which the rod-end ports 4a to 6a and the head-end ports 4b to 6b are connected switch to the second passage 27 and the tank 28. The loading spools 41a to 43a change the opening degrees according to the positions thereof. Therefore, the working fluid is supplied from each of the loading directional control valves 41 to 43 to a corresponding one of the hydraulic cylinders 4 to 6 at a flow rate corresponding to a corresponding one of the commands, in a direction corresponding to said command. This allows the loading directional control valves 41 to 43 to extend and retract the corresponding hydraulic cylinders 4 to 6 at speeds corresponding to the corresponding commands. Note that the loading directional control valves 41 to 43 are also electrically controlled directional control valves in the present embodiment.
The first travel-end pressure sensor 15 detects a first travel-end supply pressure which is a pressure being supplied to the first travel motor 2. More specifically, the first travel-end pressure sensor 15 detects the hydraulic pressure of the working fluid being supplied from the first traveling directional control valve 31 to the first travel motor 2. In the present embodiment, the first travel-end pressure sensor 15 is provided on each of the supply/drainage ports 2a, 2b of the first travel motor 2. The first travel-end pressure sensor 15 outputs the hydraulic pressure detected at the supply/drainage ports 2a, 2b of the first travel motor 2.
The second travel-end pressure sensor 16, which is a sensor different from the first travel-end pressure sensor 15, detects a second travel-end supply pressure which is a pressure being supplied to the second travel motor 3. More specifically, the second travel-end pressure sensor 16 detects the hydraulic pressure of the working fluid being supplied from the second traveling directional control valve 32 to the second travel motor 3. In the present embodiment, the second travel-end pressure sensor 16 is provided on each of the supply/drainage ports 3a, 3b of the second travel motor 3. The second travel-end pressure sensor 16 outputs the hydraulic pressure detected at the supply/drainage ports 3a, 3b of the second travel motor 3.
The loading-end pressure sensors 18 to 20 detect loading-end supply pressures which are pressures being supplied to the hydraulic cylinders 4 to 6. More specifically, each of the loading-end pressure sensors 18 to 20 detects a supply pressure being supplied to a corresponding one of the boom cylinder 4, the arm cylinder 5, and the bucket cylinder 6. In the present embodiment, the loading-end pressure sensors 18 to 20 are connected to the rod-end ports 4a to 6a and the head-end ports 4b to 6b of the hydraulic cylinders 4 to 6. The loading-end pressure sensors 18 to 20 output the hydraulic pressures detected at the rod-end ports 4a to 6a and the head-end ports 4b to 6b of the hydraulic cylinders 4 to 6.
The travel system operation device 21 is a device for an operator to operate the travel motors 2, 3. The travel system operation device 21 includes a traveling operation lever 21a which is, for example, an operation tool. The traveling operation lever 21a can be tilted. In the present embodiment, the traveling operation lever 21a can be tilted in all directions, for example. The travel system operation device 21 outputs a travel operation command corresponding to the direction of tilt and the amount of tilt. Note that the operation tool included in the travel system operation device 21 may be an operation pedal, and the form thereof is not limited.
The loading system operation device 22 is a device for an operator to operate an attachment (that is a bucket in the present embodiment). More specifically, an operation tool in the loading system operation device 22 includes a loading operation lever 22a. The loading operation lever 22a can be tilted. In the present embodiment, the loading operation lever 22a can be tilted in the depth direction, for example. The loading system operation device 22 outputs a loading operation command corresponding to the direction of tilt and the amount of tilt. Note that the operation tool included in the loading system operation device 22 is not limited to the loading operation lever 22a and may be in other forms such as an operation panel.
The control device 17 controls the operation of the travel system hydraulic circuit 13. More specifically, the control device 17 obtains the travel operation command that is output from the travel system operation device 21. Accordingly, the control device 17 controls the movement of the first traveling directional control valve 31 and the second traveling directional control valve 32 (specifically, the positions of the spools 31a, 32a) according to the travel operation command. In the present embodiment, the control device 17 outputs the first travel command and the second travel command according to the travel operation command. As a result, the first travel motor 2 and the second travel motor 3 rotate at rotational speeds corresponding to the travel operation command, in directions corresponding to the travel operation command, and thus the hydraulic excavator moves at a speed corresponding to the travel operation command, in a direction corresponding to the travel operation command.
The control device 17 controls the operation of the loading system hydraulic circuit 14. More specifically, the control device 17 obtains the loading operation command that is output from the loading system operation device 22. Accordingly, the control device 17 controls the movement of the loading directional control valves 41 to 43 (specifically, the positions of the spools 41a to 43a) according to the loading operation command. In the present embodiment, the control device 17 outputs the boom command, the arm command, and the bucket command according to the loading operation command. Accordingly, the hydraulic cylinders 4 to 6 are extended and retracted at speeds corresponding to the loading operation command. Thus, it is possible to move the bucket at a speed corresponding to the loading operation command, in a direction corresponding to the loading operation command, allowing the hydraulic excavator to perform a predetermined task.
The control device 17 outputs the opening degree signal to the flow dividing valve 12. Thus, the control device 17 controls the opening degree of the first passage 26 and the opening degree of the second passage 27 according to the travel-end supply pressures detected by the travel-end pressure sensors 15, 16 and the loading-end supply pressures detected by the loading-end pressure sensors 18 to 20. More specifically, the control device 17 obtains the travel-end supply pressure and the loading-end supply pressure. In the present embodiment, the control device 17 selectively obtains the first travel-end supply pressure and the second travel-end supply pressure from the hydraulic pressures detected by the travel-end pressure sensors 15, 16. The control device 17 estimates a port serving as a supply end among the supply/drainage ports 2a, 2b, 3a, 3b on the basis of the travel operation command, for example. The control device 17 obtains, as the first travel-end supply pressure and the second travel-end supply pressure, the hydraulic pressures at the ports serving as the supply end. The control device 17 selectively obtains the loading-end supply pressures of the hydraulic cylinders 4 to 6 in substantially the same manner from the hydraulic pressures detected by the loading-end pressure sensors 18 to 20. Furthermore, the control device 17 outputs the opening degree signal according to the first travel-end supply pressure, the second travel-end supply pressure, and the loading-end supply pressures of the hydraulic cylinders 4 to 6 that have been obtained. Thus, the flow dividing spool 12a moves to a position corresponding to the first travel-end supply pressure, the second travel-end supply pressure, and the loading-end supply pressures of the hydraulic cylinders 4 to 6. Therefore, the opening degree of the first passage 26 and the opening degree of the second passage 27 are controlled according to the first travel-end supply pressure, the second travel-end supply pressure, and the loading-end supply pressure.
For example, when the maximum value of the two travel-end supply pressures is greater than or equal to a predetermined travel-end threshold value, the control device 17 restricts the opening degree of the second passage 27. When the maximum value of the two travel-end supply pressures is less than the travel-end threshold value and the maximum value of the three loading-end supply pressures is greater than or equal to a loading-end threshold value, the control device 17 restricts the opening degree of the first passage 26. When the maximum value of the three loading-end supply pressures is less than the loading-end threshold value, the control device 17 restricts the opening degree of the second passage 27. Note that the travel-end threshold value and the loading-end threshold value are set in the control device 17 in advance. Furthermore, the travel-end threshold value and the loading-end threshold value are set in such a manner as to be adjustable, for example.
Furthermore, the control device 17 changes the position of the flow dividing spool 12a according to the first travel-end supply pressure, the second travel-end supply pressure, and the three loading-end supply pressures on the basis of the program, etc., set in advance. Thus, each of the passages 26, 27 is controlled to have an opening degree corresponding to the first travel-end supply pressure, the second travel-end supply pressure, and the three loading-end supply pressures. The control device 17 can change the opening degrees of the passages 26, 27 that are opened in relation to the first travel-end supply pressure, the second travel-end supply pressure, and the loading-end supply pressures of the hydraulic cylinders 4 to 6. More specifically, the control device 17 adjusts the command values of commands that are output according to the first travel-end supply pressure, the second travel-end supply pressure, and the loading-end supply pressures of the hydraulic cylinders 4 to 6. Thus, for example, the opening degrees of the passages 26, 27 that are open according to the first travel-end supply pressure and the second travel-end supply pressure can be adjusted according to the loading-end supply pressure.
In the hydraulic drive apparatus 1, when the traveling operation lever 21a of the travel system operation device 21 is operated solely, the travel system operation device 21 outputs the travel operation command. Accordingly, the control device 17 actuates the traveling directional control valves 31, 32 and controls the flow of the working fluid to the travel motors 2, 3 so that the working fluid flows (in the present embodiment, at a flow rate in a flow direction) according to the travel operation command. Thus, the control device 17 can cause the hydraulic excavator to perform a travel operation corresponding to the operation of the traveling operation lever 21a. Note that when the working fluid is supplied to the travel motors 2, 3 and the maximum value of the first travel-end supply pressure and the second travel-end supply pressure becomes greater than or equal to the travel-end threshold value, the flow dividing spool 12a of the flow dividing valve 12 moves to the second position A2. As a result, the first passage 26 is opened, and the opening degree of the second passage 27 is restricted.
Next, in the hydraulic drive apparatus 1, when the loading operation lever 22a of the loading system operation device 22 is operated solely, the loading system operation device 22 outputs the loading operation command. Accordingly, the control device 17 actuates the loading directional control valves 41 to 43 and controls the flow of the working fluid to the hydraulic cylinders 4 to 6 so that the working fluid flows (in the present embodiment, at a flow rate in a flow direction) according to the loading operation command. Thus, the control device 17 can cause the bucket to perform an operation corresponding to the operation of the loading operation lever 22a. Note that when the maximum value of the first travel-end supply pressure and the second travel-end supply pressure becomes less than the travel-end threshold value and the maximum value of the three loading-end supply pressures becomes greater than or equal to the predetermined loading-end threshold value, the flow dividing spool 12a of the flow dividing valve 12 is held at the first position A1. As a result, the second passage 27 is opened, and the opening degree of the first passage 26 is restricted.
Furthermore, when the traveling operation lever 21a and the loading operation lever 22a are operated at the same time, the hydraulic drive apparatus 1 operates as follows. Specifically, the control device 17 actuates the flow dividing valve 12 on the basis of the travel-end supply pressure and the loading-end supply pressure obtained. For example, when the maximum value of the two travel-end supply pressures is greater than or equal to the travel-end threshold value, the control device 17 causes the flow dividing spool 12a of the flow dividing valve 12 to move to the second position A2. As a result, the first passage 26 is opened, and the opening degree of the second passage 27 is restricted. Therefore, the deficiency in the supply of the working fluid to the travel motors 2, 3 is reduced. The second passage 27 is controlled to have an opening degree corresponding to the travel-end supply pressure and the loading-end supply pressure. Therefore, the loading system hydraulic circuit 14 can also be supplied with an appropriate amount of the working fluid. On the other hand, when the maximum value of the two travel-end supply pressures is less than the travel-end threshold value and the maximum value of the loading-end supply pressure is greater than or equal to the loading-end threshold value, the control device 17 holds the flow dividing spool 12a of the flow dividing valve 12 at the first position A1. As a result, the second passage 27 is opened, and the opening degree of the first passage 26 is restricted, meaning that the deficiency in the supply of the working fluid to the hydraulic cylinders 4 to 6 is reduced.
In the hydraulic drive apparatus 1 according to Embodiment 1, the control device 17 outputs the opening degree signal to the flow dividing valve 12 and thereby controls the opening degree of the first passage 26 and the opening degree of the second passage 27 according to the travel-end supply pressure. Therefore, by changing the control logic of the control device 17, it is possible to easily adjust the opening degrees of the first passage 26 and the second passage 27 that are opened in relation to the travel-end supply pressure. For example, the control device 17 easily adjusts the travel-end threshold value and the loading-end threshold value and easily adjusts the opening degree of the passage to be opened in relation to the travel-end supply pressure. Thus, it is possible to improve the degree of freedom of control regarding the opening degree of the first passage 26.
In the hydraulic drive apparatus 1 according to Embodiment 1, the control device 17 controls the opening degree of the first passage 26 and the opening degree of the second passage 27 according to the travel-end supply pressure and the loading-end supply pressure. Therefore, the control device 17 can adjust, according to the loading-end supply pressure, the opening degrees of the first passage 26 and the second passage 27 to be restricted in relation to the travel-end supply pressure. Thus, the flow rate of the working fluid flowing to the travel system hydraulic circuit 13 can be adjusted according to the situations of the loading actuators 4 to 6.
In the hydraulic drive apparatus 1 according to Embodiment 1, it is possible to restrict the opening degree of the first passage 26 and the opening degree of the second passage 27 by moving the flow dividing spool 12a. Therefore, the opening degrees of the first passage 26 and the second passage 27 can be easily controlled.
In the hydraulic drive apparatus 1 according to Embodiment 1, the control device 17 controls the opening degree of the first passage 26 and the opening degree of the second passage 27 according to the first travel-end supply pressure and the second travel-end supply pressure. Therefore, even when the travel system hydraulic circuit 13 supplies the working fluid to the two travel motors 2, 3, it is possible to improve the degree of freedom of control regarding the opening degree of the first passage 26 leading to the travel motors 2, 3.
In the hydraulic drive apparatus 1 according to Embodiment 1, the first travel-end pressure sensor 15 detects the hydraulic pressure of the working fluid being supplied from the first traveling directional control valve 31 to the first travel motor 2. The second travel-end pressure sensor 16 detects the hydraulic pressure of the working fluid being supplied from the second traveling directional control valve 32 to the second travel motor 3. Therefore, it is possible to easily obtain the supply pressure of the working fluid being supplied to each of the travel motors 2, 3.
In the hydraulic drive apparatus 1 according to Embodiment 1, the control device 17 controls the opening degree of the first passage 26 and the opening degree of the second passage 27 according to the travel-end supply pressure and the plurality of loading-end supply pressures. Therefore, the control device 17 controls the opening degree of the first passage 26 and the opening degree of the second passage 27 according to the travel-end supply pressure and the three loading-end supply pressures. Therefore, the control device 17 can adjust, according to the plurality of loading-end supply pressures, the opening degrees of the first passage 26 and the second passage 27 to be restricted in relation to the travel-end supply pressure. Thus, the flow rate of the working fluid flowing to the travel system hydraulic circuit 13 can be adjusted according to the situation of each of the loading actuators 4 to 6.
In the hydraulic drive apparatus 1 according to Embodiment 1, each of the plurality of loading-end pressure sensors 18 to 20 detects the supply pressure of the working fluid being supplied from a corresponding one of the loading directional control valves 41 to 43 to a corresponding one of the hydraulic cylinders 4 to 6. Therefore, it is possible to easily obtain the supply pressure of the working fluid being supplied to each of the hydraulic cylinders 4 to 6.
In the hydraulic drive apparatus 1 according to Embodiment 1, the control device 17 actuates the flow dividing valve 12 on the basis of the maximum value of the plurality of loading- end supply pressures and the maximum value of the first and second travel-end supply pressures. Therefore, the control device 17 can adjust the opening degrees of the first passage 26 and the second passage 27 according to the highest supply pressure at the travel motors 2, 3 and the hydraulic cylinders 4 to 6. Therefore, the control device 17 can adjust, according to the maximum pressure among the three loading-end supply pressures, the opening degrees of the first passage 26 and the second passage 27 to be restricted in relation to the travel-end supply pressure. Thus, the flow rate of the working fluid flowing to the travel system hydraulic circuit 13 can be adjusted according to the highest load among loads on the loading actuators 4 to 6.
A hydraulic drive apparatus 1A according to Embodiment 2 has a configuration similar to the configuration of the hydraulic drive apparatus 1 according to Embodiment 1. Therefore, the configuration of the hydraulic drive apparatus 1A according to Embodiment 2 will be described focusing on differences from the hydraulic drive apparatus 1 according to Embodiment 1; elements that are the same as those of the hydraulic drive apparatus 1 according to Embodiment 1 share the same reference signs, and as such, description of the elements will be omitted. The same applies to a hydraulic drive apparatus 1B according to Embodiment 3 to be described later.
As illustrated in
The opening degree of the first passage 26 is greatest when the flow dividing spool 12Aa is located between the second position A2 and the third position A3. As the flow dividing spool 12Aa moves from the third position A3 to the first position A1, the opening degree of the first passage 26 is restricted according to the stroke length of the flow dividing spool 12Aa. On the other hand, the opening degree of the second passage 27 is greatest when the flow dividing spool 12Aa is located between the first position A1 and the third position A3. As the flow dividing spool 12Aa moves from the third position A3 to the second position A2, the opening degree of the second passage 27 is restricted according to the stroke length of the flow dividing spool 12Aa. This means that with the flow dividing spool 12Aa at the third position A3, each of the first passage 26 and the second passage 27 has the greatest opening degree.
In the hydraulic drive apparatus 1A according to Embodiment 2, the opening degree of each of the first passage 26 and the second passage 27 increases as the flow dividing spool 12Aa moves to the third position A3. Therefore, the pressure loss at the flow dividing valve 12 can be reduced.
The hydraulic drive apparatus 1A according to Embodiment 2 produces substantially the same advantageous effects as the advantageous effects produced by the hydraulic drive apparatus 1 according to Embodiment 1.
A hydraulic drive apparatus 1B according to Embodiment 3 includes the hydraulic pump 11, the flow dividing valve 12, a travel system hydraulic circuit 13B, the loading system hydraulic circuit 14, a supply pressure selection circuit 30, a travel-end pressure sensor 15B, and a control device 17B. More specifically, the hydraulic drive apparatus 1B further includes the loading-end pressure sensors 18 to 20, the travel system operation device 21, and the loading system operation device 22. The travel system hydraulic circuit 13B includes a first traveling directional control valve 31B and a second traveling directional control valve 32B.
The first traveling directional control valve 31B is connected to a first intermediate passage 34. The first intermediate passage 34 is connected to the first passage 26 via the first traveling directional control valve 31B. The first traveling directional control valve 31B controls the opening degree between the first intermediate passage 34 and the first passage 26 according to the position of the first traveling spool 31a. Therefore, the first travel-end supply pressure is output to the first intermediate passage 34. The first intermediate passage 34 is connected to one of the two supply/drainage ports 2a, 2b of the first travel motor 2 in addition to the first passage 26. More specifically, the first intermediate passage 34 is connected to one of the supply/drainage ports 2a, 2b according to the position of the first traveling spool 31a. Note that the other of the supply/drainage ports 2a, 2b is connected to the tank 28.
The second traveling directional control valve 32B is connected to a second intermediate passage 35. The second intermediate passage 35 is connected to the first passage 26 via the second traveling directional control valve 32B. The second traveling directional control valve 32B controls the opening degree between the second intermediate passage 35 and the first passage 26 according to the position of the second traveling spool 32a. Therefore, the second travel-end supply pressure is output to the second intermediate passage 35. The second intermediate passage 35 is connected to one of the two supply/drainage ports 3a, 3b of the second travel motor 3 in addition to the first passage 26. More specifically, the second intermediate passage 35 is connected to one of the supply/drainage ports 3a, 3b according to the position of the second traveling spool 32a. Note that the other of the supply/drainage ports 3a, 3b is connected to the tank 28.
The supply pressure selection circuit 30 includes two check valves 30a, 30b. The supply pressure selection circuit 30 is connected to the first intermediate passage 34 and the second intermediate passage 35. The supply pressure selection circuit 30 obtains the first travel-end supply pressure and the second travel-end supply pressure from the intermediate passages 34, 35. The supply pressure selection circuit 30 selects and outputs the higher one of the first travel-end supply pressure and the second travel-end supply pressure.
One of the check valves, namely, the check valve 30a, is connected to the first intermediate passage 34, and the other of the check valves, namely, the check valve 30b, is connected to the second intermediate passage 35. The two check valves 30a, 30b are connected to each other on the downstream side. Each of the two check valves 30a, 30b allows the working fluid to flow in one direction from a corresponding one of the intermediate passages 34, 35 to the merge point, and blocks the opposite flow of the working fluid. Therefore, the supply pressure selection circuit 30 selects and outputs the higher one of the first travel-end supply pressure and the second travel-end supply pressure at the two check valves 30a, 30b.
The first travel-end pressure sensor 15B is connected to the supply pressure selection circuit 30. The supply pressure selection circuit 30 outputs the higher one of the first travel-end supply pressure and the second travel-end supply pressure to the first travel-end pressure sensor 15B. Therefore, on the basis of the supply pressure that is output from the supply pressure selection circuit 30, the first travel-end pressure sensor 15B detects a supply pressure that is the higher one of the first travel-end supply pressure and the second travel-end supply pressure.
Similar to the control device 17, the control device 17B controls the operations of the travel system hydraulic circuit 13B and the loading system circuit 14. The control device 17B outputs the opening degree signal to the flow dividing valve 12 according to the travel-end supply pressure detected by the travel-end pressure sensor 15B and the loading-end supply pressures detected by the loading-end pressure sensors 18 to 20. Therefore, the flow dividing spool 12a moves to a position corresponding to the travel-end supply pressure detected by the travel-end pressure sensor 15B and the loading-end supply pressures detected by the loading-end pressure sensors 18 to 20.
The hydraulic drive apparatus 1B according to Embodiment 3 performs substantially the same operation as the hydraulic drive apparatus 1 according to Embodiment 1.
In the hydraulic drive apparatus 1B according to Embodiment 3, the supply pressure selection circuit 30 selects the higher one of the first travel-end supply pressure and the second travel-end supply pressure, and outputs the selected travel-end supply pressure to the travel-end pressure sensor 15A. Therefore, the number of travel-end pressure sensors 15A can be reduced.
The hydraulic drive apparatus 1B according to Embodiment 3 produces substantially the same advantageous effects as those produced in Embodiment 1.
The hydraulic drive apparatuses 1, 1A, 1B according to Embodiments 1 to 3 include two travel motors 2, 3 to which the travel system hydraulic circuit 13 supplies the working fluid; however, there may be a single travel motor to which the travel system hydraulic circuit 13 supplies the working fluid, meaning that the number of travel motors is not limited. Similarly, the number of loading actuators to which the loading system hydraulic circuit 14 supplies the working fluid is not limited. Furthermore, the loading actuator to which the loading system hydraulic circuit 14 supplies the working fluid is not limited to the hydraulic cylinder and may be a hydraulic motor.
Furthermore, the structures of the travel system hydraulic circuits 13, 13B and the loading system hydraulic circuit 14 in the hydraulic drive apparatuses 1, 1A, 1B according to Embodiments 1 to 3 are not limited to those described above. It is sufficient that the travel system hydraulic circuits 13, 13B and the loading system hydraulic circuit 14 be circuits capable of supplying the working fluid to the travel motors 2, 3 and the hydraulic cylinders 4 to 6. Moreover, in the hydraulic drive apparatuses 1, 1A, 1B, the control devices 17, 17B may operate the travel motors 2, 3 and the loading actuators 4 to 6 according to the program stored in advance. The control devices 17, 17B obtain the hydraulic pressures directly from the travel-end pressure sensors 15, 16, 15B and the loading-end pressure sensors 18 to 20, but may obtain the hydraulic pressures indirectly, for example, via a device not illustrated in the drawings.
Hydraulic drive apparatuses 1C, 1D may be configured as follows. Specifically, as illustrated in
As illustrated in
From the foregoing description, many modifications and other embodiments of the present invention would be obvious to a person having ordinary skill in the art. Therefore, the foregoing description should be interpreted only as an example and is provided for the purpose of teaching the best mode for carrying out the present invention to a person having ordinary skill in the art. Substantial changes in details of the structures and/or functions of the present invention are possible within the spirit of the present invention.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2022-040795 | Mar 2022 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2023/009373 | 3/10/2023 | WO |
