JP6588393B2 - Work machine - Google Patents

Description

  The present invention relates to a work machine including a front control unit that performs, for example, area limited excavation control.

  Work machines such as hydraulic excavators generally operate multiple front levers by operating multiple control lever devices in a complex manner, but they can be operated skillfully so that they do not dig beyond the excavation target surface by operating the front work device within a specified area. It is difficult for an unfamiliar operator to operate the lever device.

  2. Description of the Related Art In recent years, the field of work machines that perform front control that restricts the operation of a front work device based on the bucket position or the like is expanding. When the front control is activated, the operation of the front working device is restricted so as not to excavate the lower side of the excavation target surface. As a related technique, in Patent Document 1, a proportional solenoid valve is provided in the pilot line of the operating lever device, and the hydraulic signal output from the operating lever device is transmitted by the proportional solenoid valve so that the speed of the front working device does not exceed the limit value. A technique for reducing the pressure has been proposed.

Japanese Patent No. 3091667

  Proportional solenoid valves provided for front control usually change the pilot line flow path opening area by driving the spool, which is the valve body, by passing an excitation current, which is a command value for front control, through the electromagnetic drive unit. To control the pilot pressure. However, when the front work device is away from the excavation target surface by a certain distance or more, the front control does not work and the front control proportional solenoid valve is not controlled. Even in this scene, an exciting current normally flows through the electromagnetic drive unit of the proportional solenoid valve.

  The objective of this invention is providing the working machine which can suppress power consumption and can improve energy efficiency.

To achieve the above object, the present invention provides a vehicle body, a front work device provided on the vehicle body, a plurality of hydraulic actuators that drive the front work device, a posture detector that detects a posture of the front work device, and the hydraulic pressure A hydraulic pump that discharges hydraulic fluid that drives the actuator, a plurality of control valves that control the flow of hydraulic fluid supplied from the hydraulic pump to the corresponding hydraulic actuator, and a hydraulic signal that instructs the operation of the corresponding hydraulic actuator And a pilot pump that supplies hydraulic fluid to the operation lever device, a plurality of pilot lines that connect the operation lever device and a hydraulic drive unit of the corresponding control valve, and hydraulic pressures of the pilot pump and the control valve Multiple pump lines connecting the drive unit, front Based on a proportional solenoid valve for pressure reduction provided in at least one of a plurality of pilot lines, a proportional solenoid valve for pressure increase provided in at least one of the plurality of pump lines, and a detection signal of the attitude detector In a work machine including a controller having a front control unit that calculates a restriction command value for controlling the operation of the front work device by controlling the proportional solenoid valve, the controller includes the pressure reducing and pressure increasing proportional solenoid valves. A power-saving command value storage unit that stores a power-saving command value that is an excitation current set lower than the minimum value of the excitation current applied to the electromagnetic drive unit in the opening adjustment range, and a detection signal of the attitude detector A distance calculation unit that calculates the distance between the specific point of the front work device and the excavation target surface, and stores a preset distance for the distance between the specific point and the excavation target surface And a setting distance storage unit, a large whether the distance determination unit than the distance the set distance between the specific point and drilling the target surface, the pressure or the position detector of the hydraulic signal of the operating lever device A speed calculation unit that calculates an operation speed of the hydraulic actuator based on a detection signal, a set speed storage unit that stores a preset set speed for the operation speed of the hydraulic actuator, and the hydraulic pressure calculated by the speed calculation unit A speed determination unit that determines whether or not an operation speed of the actuator is greater than the set speed; and the distance determination unit determines that the distance between the specific point and the excavation target surface is greater than the set distance , and the speed When the determination unit determines that the operating speed of the hydraulic actuator is lower than the set speed , the power saving command value read from the power saving command value storage unit is the ratio. Example: A command value is output to at least one of the pressure reducing and pressure increasing proportional solenoid valves based on the command value determining unit determined as a command value for the solenoid valve and the command value determined by the command value determining unit And an output unit.

  According to the present invention, power consumption can be suppressed and energy efficiency can be improved.

1 is a perspective view illustrating an appearance of a hydraulic excavator that is a work machine according to an embodiment of the present invention. It is a figure which shows the hydraulic drive unit with which the hydraulic shovel shown in FIG. 1 was equipped with a controller unit. FIG. 2 is a hydraulic circuit diagram of a front control hydraulic unit provided in the hydraulic excavator shown in FIG. 1. It is a functional block diagram of the controller unit with which the work machine concerning one embodiment of the present invention was equipped. It is a functional block diagram of the command value control part with which the controller unit shown in FIG. 4 was equipped. It is a characteristic view showing the relationship between the command signal and opening degree of the proportional solenoid valve for pressure reduction provided in the hydraulic excavator shown in FIG. It is a characteristic view showing the relationship between the command signal and opening degree of the proportional solenoid valve for pressure increase with which the hydraulic excavator shown in FIG. 1 was equipped. It is explanatory drawing of the calculation method of the distance of the specific point of a front work apparatus, and the excavation target surface by the distance calculating part with which the command value control part shown in FIG. 5 was equipped. It is a flowchart showing the determination procedure of the command signal by the command value control part shown in FIG.

  Embodiments of the present invention will be described below with reference to the drawings.

1. Work Machine FIG. 1 is a perspective view showing an appearance of a work machine according to an embodiment of the present invention. In the present embodiment, a hydraulic excavator equipped with a bucket as an attachment at the tip of the front working device will be described as an example of a working machine. However, the present invention can also be applied to other types of work machines such as hydraulic excavators and bulldozers equipped with attachments other than buckets. Thereafter, the front side (upper left side in FIG. 1), rear side (lower right side), left side (lower left side), and right side (upper right side) viewed from the operator seated in the driver's seat are the front and rear of the excavator. , Left and right, respectively, simply referred to as front, back, left and right.

  The hydraulic excavator shown in the figure includes a vehicle body 10 and a front working device 20. The vehicle body 10 includes a lower traveling body 11 and an upper swing body 12.

  The lower traveling body 11 includes left and right crawlers (traveling driving bodies) 13 having endless track tracks in the present embodiment, and travels by driving the left and right crawlers 13 by left and right traveling motors 35, respectively. For example, a hydraulic motor is used as the travel motor 35.

  The upper swing body 12 is a swing body provided on the lower traveling body 11 so as to be swingable via a swing device (not shown). A driver's cab 14 in which an operator is boarded is provided at the front of the upper swing body 12 (the front left side in the present embodiment). On the rear side of the cab 14 in the upper swing body 12, a power chamber 15 accommodating an engine, a hydraulic drive device and the like is mounted, and a counterweight 16 for adjusting the balance in the front-rear direction of the airframe is mounted at the rearmost portion. The turning device that connects the upper swing body 12 to the lower traveling body 11 includes a swing motor 34 (FIG. 2), and the upper swing body 12 is driven to swing relative to the lower traveling body 11 by the swing motor 34. The For example, a hydraulic motor is used as the swing motor 34.

  The front work device 20 is a device for performing work such as excavation of earth and sand, and is provided at the front portion of the upper swing body 12 (right side of the cab 14 in this embodiment). The front work device 20 is an articulated work device including a boom 21, an arm 22, and a bucket 23. The boom 21 is connected to the frame of the upper swing body 12 by pins (not shown) extending left and right, and is also connected to the upper swing body 12 by a boom cylinder 31. The boom 21 is configured to rotate up and down with respect to the upper swing body 12 as the boom cylinder 31 expands and contracts. The arm 22 is connected to the tip of the boom 21 by a pin (not shown) extending left and right, and is also connected to the boom 21 by an arm cylinder 32. The arm 22 rotates with respect to the boom 21 as the arm cylinder 32 expands and contracts. The bucket 23 is connected to the tip of the arm 22 by a pin (not shown) extending horizontally and horizontally, and is also connected to the arm 22 by a bucket cylinder 33. The bucket 23 rotates with respect to the arm 22 as the bucket cylinder 33 expands and contracts. The boom cylinder 31, the arm cylinder 32, and the bucket cylinder 33 are hydraulic cylinders that drive the front working device 20.

  In addition, the hydraulic excavator is provided with a detector for detecting information related to the position and orientation in place. For example, angle detectors 8 a to 8 c are provided at the respective rotation fulcrums of the boom 21, the arm 22, and the bucket 23. The angle detectors 8a to 8c are used as posture detectors that detect information related to the position and posture of the front work device 20, and detect the rotation angles of the boom 21, the arm 22, and the bucket 23, respectively. In addition, the upper swing body 12 includes an inclination detector 8d, positioning devices 9a and 9b (FIG. 4), a radio device 9c (FIG. 4), a hydraulic drive device 30 (FIG. 2), and a controller unit 100 (FIG. 4 and the like). Is provided. The inclination detector 8d is used as a posture detection means for the upper swing body 12 that detects at least one tilt in the front-rear direction and the left-right direction of the upper swing body 12. For example, RTK-GNSS (Real Time Kinematic-Global Navigation Satellite System) is used for the positioning devices 9a and 9b, and the position information of the vehicle body 10 is acquired by the positioning devices 9a and 9b. The wireless device 9c receives correction information from a reference station GNSS (not shown). The positioning devices 9a and 9b and the wireless device 9c are means for detecting the position and orientation of the upper swing body 12. Further, a switch 7 (FIG. 3) for turning on / off the control of the front control unit 120 is provided in any one lever portion of the operation panel (not shown) in the cab 14 or the operation lever devices 51 to 54 (FIG. 2 and the like). Reference) is provided. The hydraulic drive device 30 and the controller unit 100 will be described next.

2. Hydraulic Drive Device FIG. 2 is a view showing a hydraulic drive device provided in the hydraulic excavator shown in FIG. 1 together with a controller unit. For those already described, the same reference numerals as those in the above-mentioned drawings are given in FIG.

  The hydraulic drive device 30 is a device that drives a driven member of a hydraulic excavator and is accommodated in the power chamber 15. The driven members include the front work device 20 (the boom 21, the arm 22, and the bucket 23) and the vehicle body 10 (the crawler 13 and the upper swing body 12). The hydraulic drive device 30 includes hydraulic actuators 31 to 34, a hydraulic pump 36, control valves 41 to 44, a pilot pump 37, operation lever devices 51 to 54, a front control hydraulic unit 60, and the like.

2-1. Hydraulic Actuators Hydraulic actuators 31 to 34 are generic names for the boom cylinder 31, the arm cylinder 32, the bucket cylinder 33, and the swing motor 34. The travel motor 35 is not shown in FIG. When there are a plurality of boom cylinders 31, arm cylinders 32, bucket cylinders 33, and swing motors 34, they may be collectively referred to as “hydraulic actuators 31 to 34”, “hydraulic actuators 31, 32”, and the like. The hydraulic actuators 31 to 35 are driven by hydraulic oil discharged from the hydraulic pump 36.

2-2. Hydraulic Pump The hydraulic pump 36 is a variable displacement pump that discharges hydraulic oil that drives the hydraulic actuators 31 to 34 and the like, and is driven by the prime mover 17. The prime mover 17 in this embodiment is an engine that converts combustion energy into power, such as an internal combustion engine. Although only one hydraulic pump 36 is illustrated in FIG. 2, a plurality of hydraulic pumps 36 may be provided. The hydraulic oil discharged from the hydraulic pump 36 flows through the discharge pipe 36a and is supplied to the hydraulic actuators 31 to 34 via the control valves 41 to 44, respectively. Each return oil from the hydraulic actuators 31 to 34 flows into the return oil pipe 36b via the control valves 41 to 44, and is returned to the tank 38. The discharge pipe 36a is provided with a relief valve (not shown) that regulates the maximum pressure of the discharge pipe 36a. Although not shown in FIG. 2, the traveling motor 35 is also driven with a similar circuit configuration. When a soil removal plate is provided on at least one of the front and rear of the lower traveling body 11, when an attachment having an actuator such as a breaker is attached to the front working device 20 instead of the bucket 23, a hydraulic actuator for the soil removal plate or the attachment Are driven with the same circuit configuration.

2-3. Among the control valves 41 to 44, the control valve 41 is for the boom cylinder, the control valve 42 is for the arm cylinder, the control valve 43 is for the bucket cylinder, and the control valve 44 is for the swing motor. A control valve for the travel motor is not shown. The control valves 41 to 44 are hydraulically driven flow rate control valves for controlling the flow (direction and flow rate) of hydraulic oil supplied from the hydraulic pump 36 to the corresponding hydraulic actuators, and hydraulic drive units to which hydraulic signals are respectively input. 45 and 46 are provided. The control valves 41 to 44 are configured to move left or right in the drawing when a hydraulic signal is input to the hydraulic drive unit 45 or 46, and return to the neutral position by the force of the spring when the input of the hydraulic signal is stopped. is there. For example, when a hydraulic signal is input to the hydraulic drive unit 45 of the boom cylinder control valve 41, the spool of the control valve 41 moves rightward by a distance corresponding to the magnitude of the hydraulic signal in FIG. As a result, hydraulic oil from the hydraulic pump 36 is supplied to the bottom side oil chamber of the boom cylinder 31 at a flow rate corresponding to the hydraulic signal, and the boom cylinder 31 extends and the boom 21 is raised at a speed corresponding to the magnitude of the hydraulic signal. .

2-4. Pilot Pump The pilot pump 37 is a fixed displacement pump that discharges hydraulic oil that drives control valves such as the control valves 41 to 44, and is driven by the prime mover 17 like the hydraulic pump 36. The pump line 37a, which is a discharge pipe of the pilot pump 37, passes through the lock valve 39, and then branches into a plurality of branches connected to the valves of the operating lever devices 51 to 54 and the front control hydraulic unit 60. The hydraulic oil discharged from the pilot pump 37 through the pump line 37a is supplied to the operation lever devices 51 to 54. The branched pump lines 37a are connected to the hydraulic drive unit of a specific control valve (control valves 41 and 43 in this embodiment).

  The lock valve 39 is an electromagnetic switching valve in this example, and its electromagnetic drive unit is electrically connected to a position detector of a gate lock lever (not shown) disposed in the cab 14 (FIG. 1). . The gate lock lever is a bar installed on the driver's boarding side of the driver's seat so as to prevent the operator from getting off in the closed position, and to get off, the gate lock lever must be pulled up to open the driver's seat It is supposed not to be. As the position of the gate lock lever, the laid position is described as the “lock release position” of the operation system, and the raised position is described as the “lock position” of the operation system. The position of the gate lock lever is detected by a position detector, and a signal corresponding to the position of the gate lock lever is input to the lock valve 39 from the position detector. If the gate lock lever is in the locked position, the lock valve 39 is closed and the pump line 37a is shut off, and if it is in the unlocked position, the lock valve 39 is opened and the pump line 37a is opened. In the state where the pump line 37a is cut off, the original pressure of the operating lever devices 51 to 54 is cut off, so that no hydraulic signal is input to the control valves 41 to 44 regardless of whether or not there is an operation. That is, the operation by the operation lever devices 51 to 54 is invalidated, and operations such as turning and excavation are prohibited.

2-5. Operation Lever Device The operation lever devices 51 to 54 are lever operation type operation devices that generate and output hydraulic signals instructing the operations of the corresponding hydraulic actuators 31 to 34 according to the operations. ). Among the operation lever devices 51 to 54, the operation lever device 51 is for boom operation, the operation lever device 52 is for arm operation, the operation lever device 53 is for bucket operation, and the operation lever device 54 is for turning operation. In the case of a hydraulic excavator, the operation lever devices 51 to 54 are generally cross-operated lever devices, and one hydraulic actuator is operated by a tilting operation in the front-rear direction, and another hydraulic actuator is operated by a tilting operation in the left-right direction. Can be instructed. Accordingly, the four operation lever devices 51 to 54 are divided into two groups each including two, and each group shares one lever portion. Accordingly, the lever portions of the operating lever devices 51 to 54 are two in total for right-hand operation and left-hand operation, and when the switch 7 described above is provided in the lever portion, it is provided in at least one of the two lever portions. become. The operating lever device for traveling is not shown.

  The boom operating lever device 51 includes a boom raising command signal output valve 51a and a boom lowering command signal output valve 51b. A pump line 37a is connected to the input ports (primary ports) of the signal output valves 51a and 51b. The output port (secondary port) of the boom output command signal output valve 51a is connected to the hydraulic drive unit 45 of the boom cylinder control valve 41 via pilot lines 51a1 and 51a2. The output port of the boom lowering command signal output valve 51b is connected to the hydraulic drive unit 46 of the control valve 41 via the pilot line 51b1. For example, when the operation lever device 51 is tilted to the boom raising command side, the signal output valve 51a opens at an opening corresponding to the operation amount. As a result, the hydraulic oil discharged from the pilot pump 37 input from the pump line 37a is decompressed according to the operation amount by the signal output valve 51a and is output as a hydraulic signal to the hydraulic drive unit 45 of the control valve 41. The pilot lines 51a1 and 51b1 are provided with pressure detectors 6a and 6b, respectively. The magnitudes (pressure values) of the pressure signals output from the signal output valves 51a and 51b are detected by the pressure detectors 6a and 6b. It has become so.

  Similarly, the arm operating lever device 52 includes an arm cloud command signal output valve 52a and an arm dump command signal output valve 52b. The bucket operation lever device 53 includes a bucket cloud command signal output valve 53a and a bucket dump command signal output valve 53b. The operation lever device 54 for turning operation includes a signal output valve 54a for a right turn command and a signal output valve 54b for a left turn command. The input ports of the signal output valves 52a, 52b, 53a, 53b, 54a, 54b are connected to the pump line 37a. The output ports of the signal output valves 52a and 52b of the arm operating lever device 52 are connected to the hydraulic drive units 45 and 46 of the arm cylinder control valve 42 via pilot lines 52a1 and 52b1, respectively. The output port of the bucket cloud command signal output valve 53a is connected to the hydraulic drive unit 45 of the bucket cylinder control valve 43 through pilot lines 53a1 and 53a2. The output port of the bucket dump command signal output valve 53b is connected to the hydraulic drive unit 46 of the control valve 43 via the pilot lines 53b1 and 53b2. The output ports of the signal output valves 54a and 54b of the operation lever device 54 for turning operation are connected to the hydraulic drive portions 45 and 46 of the control valve 44 for the turning motor via pilot lines 54a1 and 54b1, respectively. The hydraulic signal output principle of the operation lever devices 52 to 54 is the same as that of the operation lever device 51 for boom operation.

  In the present embodiment, the shuttle block 47 is provided in the middle of the pilot lines 51a2, 51b1, 52a1, 52b1, 53a2, 53b2, 54a1, and 54b1. The hydraulic signal output from the operation lever devices 51 to 54 is also input to the regulator 48 of the hydraulic pump 36 via the shuttle block 47. Although a detailed configuration of the shuttle block 47 is omitted, the discharge flow rate of the hydraulic pump 36 is controlled in accordance with the hydraulic pressure signal by inputting the hydraulic pressure signal to the regulator 48 via the shuttle block 47.

2-6. Front Control Hydraulic Unit The front control hydraulic unit 60 increases or decreases the hydraulic pressure signal output from the operation lever devices 51 to 53 according to the situation so that the front work device 20 does not excavate beyond the excavation target surface. Hardware. The front control hydraulic unit 60 is driven by a signal from the controller unit 100.

  FIG. 3 is a hydraulic circuit diagram of the front control hydraulic unit. In the figure, the elements denoted by the same reference numerals as those in the other drawings are the same as the elements illustrated in the other drawings. The front control hydraulic unit 60 includes pressure reducing proportional solenoid valves 61b, 62a, 62b, 63a, 63b, pressure increasing proportional solenoid valves 71a, 73a, 73b, a shutoff valve 70, and shuttle valves 91-93.

Shuttle valve The shuttle valves 91 to 93 are high pressure selection valves, each having two inlet ports and one outlet port. One inlet port of the shuttle valve 91 is connected to the boom raising command signal output valve 51a via the pilot line 51a1, and the other inlet port is connected to the pilot pump 37 via the pump line 37a without passing through the signal output valve. Yes. The outlet port of the shuttle valve 91 is connected to the hydraulic drive unit 45 (boom raising side) of the boom cylinder control valve 41 via the pilot line 51a2. One inlet port of the shuttle valve 92 is connected to the signal output valve 53a for bucket cloud command via the pilot line 53a1, and the other inlet port is connected to the pilot pump 37 via the pump line 37a without passing through the signal output valve. Yes. The outlet port of the shuttle valve 92 is connected to the hydraulic drive unit 45 (bucket cloud side) of the bucket cylinder control valve 43 via the pilot line 53a2. One inlet port of the shuttle valve 93 is connected to the bucket dump command signal output valve 53b via the pilot line 53b1, and the other inlet port is connected to the pilot pump 37 via the pump line 37a without passing through the signal output valve. Yes. The outlet port of the shuttle valve 93 is connected to the hydraulic drive unit 46 (bucket dump side) of the control valve 43 for the bucket cylinder via the pilot line 53b2.

-Proportional solenoid valve for pressure reduction The proportional solenoid valves 61b, 62a, 62b, 63a, 63b are normally open type proportional valves. When the magnet is demagnetized, the maximum opening degree is obtained, and when excited by a signal from the controller unit 100, the signal Decrease the opening in proportion to the size (close). These are all provided in the pilot line of the corresponding signal output valve, and in order to suppress excavation below the target excavation surface, the maximum value of the hydraulic signal output from the corresponding signal output valve is set. It plays the role of limiting according to the signal from the controller unit 100. In this specification, “demagnetization” of the proportional solenoid valve means that the magnitude of the excitation current is reduced to a value that brings the proportional solenoid valve into a normal state (maximum opening for the normal open type, minimum opening for the normal closed type). This also includes stopping the output of excitation current.

  Specifically, the proportional solenoid valve 61b is provided on the pilot line 51b1 of the boom lowering command signal output valve 51b, and limits the maximum value of the boom lowering command hydraulic signal according to the signal S61b of the controller unit 100. To do. The proportional solenoid valve 62a is provided on the pilot line 52a1 of the arm cloud command signal output valve 52a, and limits the maximum value of the arm cloud command hydraulic signal according to the signal S62a of the controller unit 100. The proportional solenoid valve 62b is provided on the pilot line 52b1 of the arm dump command signal output valve 52b, and limits the maximum value of the arm dump command hydraulic signal according to the signal S62b of the controller unit 100. The proportional solenoid valve 63a is provided on the pilot line 53a1 of the bucket cloud command signal output valve 53a, and limits the maximum value of the bucket cloud command hydraulic signal in accordance with the signal S63a of the controller unit 100. The proportional solenoid valve 63b is provided on the pilot line 53b1 of the bucket dump command signal output valve 53b, and limits the maximum value of the hydraulic signal for the bucket dump command in accordance with the signal S63b of the controller unit 100.

-Proportional solenoid valve for pressure increase Proportional solenoid valves 71a, 73a, 73b are normally closed type proportional valves. When demagnetized, they have a minimum opening (zero opening), and when excited by a signal from the controller unit 100, Increase the opening in proportion to the size of (open). These are all provided in the pump line 37a connected to the shuttle valve, and play a role of bypassing the operation lever device and outputting a hydraulic signal not depending on the operation of the operation lever device according to the signal of the controller unit 100. Hydraulic signals input from the proportional solenoid valves 71a, 73a, 73b to the other inlet ports of the shuttle valves 91-93 are transmitted from the operation lever devices 51, 53 input to the one inlet port of the shuttle valves 91-93. Interferes with the hydraulic signal. In the present specification, the proportional solenoid valves 71a, 73a, and 73b are referred to as pressure-increasing proportional solenoid valves in that a hydraulic pressure signal that is higher than the hydraulic pressure signal output from the operation lever devices 51 and 53 can be output.

  Specifically, the proportional solenoid valve 71a is provided on a pump line 37a connected to the shuttle valve 91, and outputs a hydraulic signal for automatic boom raising operation according to a signal S71a of the controller unit 100. Normally, when an open command signal is output to the pressure increasing proportional solenoid valve 71a, a close command signal is output to the pressure reducing proportional solenoid valve 61b. Therefore, when the proportional solenoid valve 71a is opened, the proportional solenoid valve 61b is closed. It is like that. In this case, even if the boom lowering operation is performed, a hydraulic pressure signal is input only to the hydraulic drive unit 45 with respect to the control valve 41, and the boom raising operation is forcibly performed. This proportional solenoid valve 71a functions when excavating below the target excavation surface.

  The proportional solenoid valve 73a is provided on a pump line 37a connected to the shuttle valve 92, and outputs a hydraulic signal that instructs a bucket cloud operation according to a signal S73a of the controller unit 100. The proportional solenoid valve 73b is provided on a pump line 37a connected to the shuttle valve 93, and outputs a hydraulic pressure signal for instructing a bucket dump operation according to a signal S73b of the controller unit 100. The hydraulic signal output from the proportional solenoid valves 73 a and 73 b is a signal for correcting the attitude of the bucket 23. These hydraulic pressure signals are selected by the shuttle valves 92 and 93 and input to the control valve 43, whereby the posture of the bucket 23 is corrected so as to have a constant angle with respect to the excavation target surface.

-Shut-off valve The shut-off valve 70 is a normally closed type electromagnetically driven on-off valve (electromagnetic switching valve). When the magnet is demagnetized, the shut-off valve 70 is fully closed (zero opening) and excited by receiving a signal S70 from the controller unit 100. Open when done. This shut-off valve 70 is provided between the branch portion of the tributary connected to the shuttle valves 91 to 93 in the pump line 37a and the lock valve 39 (FIG. 2). When the shut-off valve 70 is closed by a command from the controller unit 100, generation and output of a hydraulic pressure signal that is not caused by operation of the operation lever devices 51 and 53 is prohibited.

2-7. Controller Unit FIG. 4 is a functional block diagram of the controller unit. As shown in the figure, the controller unit 100 includes functional units such as an input unit 110, a front control unit 120, a command value control unit 130, and an output unit 170. Hereinafter, each functional unit will be described.

Input unit / output unit The input unit 110 is a functional unit that inputs signals from sensors and the like. Signals from the pressure detectors 6a and 6b, the switch 7, the angle detectors 8a to 8c, the inclination detector 8d, the positioning devices 9a and 9b, the wireless device 9c, and the like are input to the input unit 110.

  The output unit 170 generates a command signal based on the command value determined through the processing of the front control unit 120 and the command value control unit 130, outputs the command signal to the front control hydraulic unit 60, and controls the corresponding valve. Part. The valves that can be controlled are the proportional solenoid valves 61b, 62a, 62b, 63a, 63b, 71a, 73a, 73b and the shutoff valve 70, and at least one of the command signals is actually output. The command signal is not necessarily output to a plurality or all of them.

Front control unit The front control unit 120 is configured to prevent the excavation from exceeding the excavation target surface (under the excavation target surface) based on the signals from the angle detectors 8a to 8c and the inclination detector 8d. It is a functional part which calculates a restriction command value that restricts the operation of The limit command value is output to the command value control unit 130. The front control is a general term for control for controlling the front control hydraulic unit 60 by the distance between the excavation target surface and a specific point of the bucket 23, the expansion / contraction speed of the hydraulic actuators 31 to 33, and the like. For example, at least one of the proportional solenoid valves 61b, 62a, 62b, 63a, and 63b for pressure reduction is controlled, and the control for decelerating the operation of at least one of the hydraulic actuators 31 to 33 near the excavation target surface is also performed on the front side. One of the controls. Automatic boom raising control for controlling at least one of the pressure increasing proportional solenoid valves 71a, 73a, 73b and forcibly raising the boom in a scene where the lower side of the excavation target surface has been excavated, Control for keeping the angle of the bucket 23 constant is also included in the front control. In addition, so-called boom lowering stop control and bucket pressure increase control are included. In addition, the one that controls at least one of the proportional solenoid valves 61b, 62a, 62b, 63a, and 63b for pressure reduction and at least one of the proportional solenoid valves 71a, 73a, and 73b for pressure increase is also the front. Included in control. Furthermore, in the present specification, so-called trajectory control for controlling the trajectory drawn by the front working device 20 to a constant trajectory is also one of the front controls. Although the details of the front control unit 120 are not described, publicly known techniques such as JP-A-8-333768 and JP-A-2006-003442 can be appropriately applied to the front control unit 120, for example.

3. Command Value Control Unit FIG. 5 is a functional block diagram of the command value control unit. As shown in the figure, the command value control unit 130 includes an input determination unit 131, a storage unit 132, a distance calculation unit 133, a distance determination unit 134, a speed calculation unit 135, a speed determination unit 136, and a command value determination unit 137. I have.

Input Determination Unit The input determination unit 131 is a functional unit that determines whether a limit command value is input from the front control unit 120. When the front control function is in the on state, for example, during a specific control target operation such as a boom lowering operation in which the bucket 23 descends, the proportional solenoid valve 61b as the bucket 23 approaches the excavation target surface. The maximum value of the pressure signal is limited by narrowing down etc. On the other hand, even when the front control function is on, the opening control of the proportional solenoid valve 61b and the like by the front control unit 120 is not executed during a non-control target operation such as a boom raising operation in which the bucket 23 is raised. Accordingly, when the distance D between a specific point (described later) of the front work device 20 and the excavation target surface S is larger than the set distance D0, and when the operation is out of the control target even when the distance D is equal to or less than the set distance D0, the front controller 120. No limit command value is output from. The restriction command value is output from the front control unit 120, for example, when the front control function is in the on state, the distance D is equal to or less than the set distance D0, and the control target operation is being performed. This is the case when the conditions are met simultaneously. The input determination unit 131 determines whether or not such a limit command value has been input.

Storage unit The storage unit 132 is a functional unit that stores various types of information. The set distance storage unit 141, the set speed storage unit 142, the excavation target surface storage unit 143, the body size storage unit 144, the standby command value storage unit 145, and the saving A power command value storage unit 146 is included.

  The set distance storage unit 141 is a storage area that stores a preset set distance D0 (> 0) for the distance D between the specific point P of the front work device 20 and the excavation target surface S. The set speed storage unit 142 is a storage area that stores a set speed V0 (> 0) predetermined for the operating speed V of a specific hydraulic actuator (for example, the boom cylinder 31). The excavation target surface storage unit 143 is a storage area in which the excavation target surface S is stored. The excavation target surface S is a target landform that is excavated (modeled) by a hydraulic excavator, and may be stored manually set in a coordinate system with the upper revolving body 12 as a reference, or may be stored in the tertiary of the earth coordinate system. In some cases, the original position information is stored in advance. The three-dimensional position information of the excavation target surface S is information obtained by adding position data to terrain data representing the excavation target surface S with polygons, and is created in advance. The body size storage unit 144 is a storage area that stores the dimensions of the front work device 20 and the upper swing body 12.

  The standby command value storage unit 145 is a storage area that stores standby command values output to the proportional solenoid valves 61b, 62a, 62b, 63a, 63b for pressure reduction. The power saving command value storage unit 146 is a power saving command that is an excitation current set smaller than the standby command value of the proportional solenoid valves 61b, 62a, 62b, 63a, 63b, 71a, 73a, 73b for pressure reduction and pressure increase. This is a storage area for storing values. The standby command value and the power saving command value will be described later.

Distance calculation unit The distance calculation unit 133 calculates the distance D between the specific point P of the front work device 20 and the excavation target surface S based on the detection signals of the angle detectors 8a to 8c input via the input unit 110. It is a functional part to do. An example of the calculation of the distance D will be described later.

Distance determination unit The distance determination unit 134 determines whether the distance D between the specific point P calculated by the distance calculation unit 133 and the excavation target surface S is larger than the set distance D0 read from the set distance storage unit 141. It is a functional part to do.

Speed calculation unit The speed calculation unit 135 calculates the operation speed V (extension / contraction speed) of a specific hydraulic actuator, in this example, the boom cylinder 31, based on the signals of the pressure detectors 6a and 6b input via the input unit 110. It is a functional part that calculates. For example, the speed calculation unit 135 includes a storage unit that stores the flow rate characteristics of the boom cylinder control valve 41 (such as the relationship between the flow rate of hydraulic fluid to circulate and the opening degree). The opening degree of the control valve 41 has a relationship corresponding to the magnitude of the hydraulic signal to the control valve 41 detected by the pressure detectors 6a and 6b. Based on this, the operation speed V of the boom cylinder 31 is calculated by the speed calculation unit 135 based on the flow characteristics of the control valve 41 and the signals of the pressure detectors 6a and 6b. Note that the speed calculator 135 selects the larger one of the signals from the pressure detectors 6a and 6b and calculates the operating speed of the boom cylinder 31 as the basis of the calculation. Depending on which signal is the basis of the calculation, it is distinguished whether the calculated operation speed V is the extension speed or the contraction speed of the boom cylinder 31. Needless to say, for example, the operation speed V calculated based on the signal of the pressure detector 6b that detects the pressure signal for the boom lowering command is the contraction speed of the boom cylinder 31 corresponding to the boom lowering operation. The contraction direction of the boom cylinder 31 is taken as the positive direction of the operation speed V, and the extension speed is handled as a negative speed.

Speed Determination Unit The speed determination unit 136 is a functional unit that determines whether the operating speed V of the boom cylinder 31 calculated by the speed calculation unit 135 is higher than the set speed V0 read from the set speed storage unit 142. .

Command Value Determination Unit The command value determination unit 137 is a functional unit that determines command values of command signals for the proportional solenoid valves 61 b, 62 a, 62 b, 63 a, 63 b, 71 a, 73 a, 73 b and outputs the command values to the output unit 170. . The command value is determined by selection from the limit command value input from the front control unit 120, the standby command value read from the standby command value storage unit 145, and the power saving command value read from the power saving command value storage unit 146. Is done. Specifically, the command signal is selected by dividing the situation into the following first to third cases.
(First case) When the input determination unit 131 determines that the limit command value is input from the front control unit 120;
(Second case) Cases other than the first case and the third case;
(Third case) When the limit command value is not input, the distance determination unit 134 determines that the distance D between the specific point P and the excavation target surface S is larger than the set distance D0, and the speed determination unit If it is determined at 136 that the operating speed V is lower than the set speed V0:
The limit command value is selected as the command value in the first case, the standby command value in the second case, and the power saving command value in the third case.

Standby command value FIG. 6 is a characteristic diagram showing the relationship between the command signal and the opening of the proportional solenoid valve for pressure reduction. As shown in the figure, the proportional solenoid valve for pressure reduction (for example, the proportional solenoid valve 61b) is narrowed down and the opening degree decreases as the command signal (excitation current in this embodiment) input to the electromagnetic drive unit increases. To do. When the magnitude of the command value changes in the range between i1 and i3 (> i1), the opening of the proportional solenoid valve changes in proportion to the magnitude of the command signal. That is, the command value i1 is a command value corresponding to the maximum opening in a range (hereinafter referred to as an opening adjustment region) with a change in the opening of the proportional solenoid valve, and the command value i3 is a minimum opening ( In this embodiment, the command value corresponds to zero opening). The range smaller than the command value i1 is a demagnetized state, and the opening degree of the proportional solenoid valve remains unchanged at the maximum. In the range larger than the command value i3, the opening degree of the proportional solenoid valve remains unchanged and remains unchanged. The standby command value is the command value i2 of the excitation current corresponding to the intermediate opening set between the maximum opening and the minimum opening of the proportional solenoid valve. The intermediate opening can be arbitrarily selected between the maximum opening and the minimum opening. For example, an average value of the maximum opening and the minimum opening can be exemplified. i2 may be set to a different value unique to each proportional solenoid valve. Further, the command value of the command signal during standby is set to i2 at least one of the proportional solenoid valves 61b, 62a, 62b, 63a, 63b, and not all of them are necessarily required.

Power saving command value FIG. 7 is a characteristic diagram showing the relationship between the command signal and the opening of the proportional solenoid valve for pressure increase. As shown in the figure, the opening degree of the proportional solenoid valve for pressure increase (for example, the proportional solenoid valve 71a) increases as the command signal (excitation current in this embodiment) input to the electromagnetic drive unit increases. When the magnitude of the command signal changes in the range of i5 and i6 (> i5), the opening degree of the proportional solenoid valve changes in proportion to the magnitude of the command signal. That is, the command value i5 is a command value corresponding to the minimum opening in the opening adjustment range of the proportional solenoid valve, and the command value i6 is a command value corresponding to the maximum opening in the opening adjustment region. The range smaller than the command value i5 is a demagnetized state, and the opening degree of the proportional solenoid valve remains unchanged with the minimum. In a range larger than the command value i6, the opening degree of the proportional solenoid valve remains unchanged at the maximum. The power saving command value is based on the minimum value of the excitation current applied in the opening adjustment range to the electromagnetic drive parts of the proportional solenoid valves 61b, 62a, 62b, 63a, 63b, 71a, 73a, 73b for pressure reduction and pressure increase. The excitation current value is also set low. Therefore, for the proportional solenoid valves 61b, 62a, 62b, 63a, 63b for pressure reduction, a command value i0 (<i1) smaller than the command value i1 in FIG. 6 is set as the power saving command value. For the pressure increasing proportional solenoid valves 71a, 73a, 73b, a command value i4 (<i5) smaller than the command value i5 in FIG. 7 is set as the power saving command value. The power saving command values i0 and i4 can be arbitrarily selected within a range smaller than the command values i1 and i5, respectively, and may be set to 0 (zero). i0 and i4 may be different values or the same value, and i0 and i4 unique to each proportional solenoid valve may be set. The command value of the command signal at the time of demagnetization is set to i0 or i4 is at least one of the proportional solenoid valves 61b, 62a, 62b, 63a, 63b, 71a, 73a, 73b, and it is not always necessary Absent.

Calculation Example of Distance between Specific Point and Excavation Target Surface FIG. 8 is an explanatory diagram of a method for calculating the distance between the specific point of the front work device and the excavation target surface by the distance calculation unit. In FIG. 8, the operation plane of the front work device 20 (plane orthogonal to the rotation axis of the boom 21 etc.) is viewed from the orthogonal direction (extension direction of the rotation axis of the boom 21 etc.). The hydraulic actuators 31 to 33 are not shown in order to prevent congestion.

  In FIG. 8, the specific point P is set at the position of the tip (toe) of the bucket 23. The specific point P is typically set at the tip of the bucket 23, but may be set at another part of the front work device 20. Signals from the angle detectors 8 a to 8 c are input to the distance calculation unit 133 via the input unit 110, and information on the excavation target surface S is input from the excavation target surface storage unit 143. In addition, when calculating the distance D in the earth coordinate system, the detection signal of the inclination detector 8d, the position information of the vehicle body 10 acquired by the positioning devices 9a and 9b, and the correction information received by the wireless device 9c are also input. The data is input to the distance calculation unit 133 via the unit 110. When obtaining the distance D in the earth coordinate system, the distance calculation unit 133 corrects the position information of the positioning devices 9a and 9b with the correction information to calculate the position and orientation of the vehicle body 10, and uses the signal from the inclination detector 8d to calculate the vehicle body 10 Calculate the slope of.

  The excavation target plane S is defined by a line of intersection with the operation plane of the front work apparatus 20, and the positional relationship between the excavation target plane S and the car body 10 is expressed in the earth coordinate system together with information such as the position, orientation, and inclination of the car body 10. Be grasped. The area above the excavation target surface S is defined as the excavation area where the movement of the specific point P is considered to be appropriate. The excavation target surface S is once defined by at least one linear expression in an XY coordinate system with a hydraulic excavator as a reference, for example. The XY coordinate system is, for example, an orthogonal coordinate system having the rotation fulcrum of the boom 21 as an origin, and an axis extending parallel to the turning center axis of the upper swing body 12 through the origin is the Y axis (upward is a positive direction). The axis that is orthogonal to the Y axis at the origin and extends forward is the X axis (the forward direction is the positive direction). When the excavation target surface S is manually set, the positional relationship between the excavation target surface S and the vehicle body 10 is known.

  The excavation target plane S defined in the XY coordinate system is defined again in the XaYa coordinate system, which is an orthogonal coordinate system of the origin O with the self as one axis (Xa axis). Needless to say, the Ya axis is an axis at the origin O and orthogonal to the Xa axis. The Xa axis has the forward direction as the positive direction, and the Ya axis has the upward direction as the positive direction.

  In the distance calculation unit 133, the dimension data (L1, L2, L3) of the front work device 20 read from the body dimension storage unit 144, and the rotation angles α, β, γ detected by the angle detectors 8a to 8c. Is used to calculate the position of the bucket specific point P. The position of the specific point P is obtained, for example, as a coordinate value (X, Y) in an XY coordinate system based on a hydraulic excavator. The coordinate value (X, Y) of the specific point P is obtained from the following equations (1) and (2).

X = L1 · sin α + L2 · sin (α + β) + L3 · sin (α + β + γ) (1)
Y = L 1 · cos α + L 2 · cos (α + β) + L 3 · cos (α + β + γ) (2)
L1 is the distance between the pivot fulcrum of the boom 21 and the arm 22, L2 is the distance between the pivot fulcrum of the arm 22 and the bucket 23, and L3 is the distance between the pivot fulcrum of the bucket 23 and the specific point P. α is the included angle between the Y axis (the portion extending upward from the origin) and the straight line 11 passing through the rotation fulcrum of the boom 21 and the arm 22 (the portion extending from the origin toward the rotation fulcrum of the arm 22). β is a straight line l1 (a portion extending from the rotation fulcrum of the arm 22 to the side opposite to the origin) and a straight line l2 passing through the rotation fulcrum of the arm 22 and the bucket 23 (from the rotation fulcrum of the arm 22 to the rotation fulcrum of the bucket 23). And the included angle. γ is an included angle between the straight line 12 (the portion extending from the rotation fulcrum of the bucket 23 to the side opposite to the rotation fulcrum of the arm 22) and the straight line 13 passing through the specific point P.

  The distance calculation unit 133 converts the coordinate value (X, Y) of the specific point P defined in the XY coordinate system as described above into the coordinate value (Xa, Ya) of the XaYa coordinate system. The Ya value of the specific point P thus obtained is the value of the distance D between the specific point P and the excavation target surface S. The distance D is a distance from the intersection of the straight line perpendicular to the excavation target surface S through the specific point P and the excavation target surface S to the specific point P, and distinguishes between positive and negative values of Ya (that is, the distance in the excavation region). D becomes a positive value, and becomes a negative value in the region below the excavation target surface S).

3. Operation First, the basic operation of the hydraulic actuator with respect to lever operation will be described by taking the processing of the command value control unit 130 into consideration.

3-1. When the front control is valid For example, when a boom lowering operation is performed with the operation lever device 51, the boom lowering command signal output valve 51b opens according to the operation amount, and the boom cylinder control valve 41 is connected via the pilot line 51b1. The hydraulic signal is input to the hydraulic drive unit 46. Thereby, the boom cylinder 31 contracts and the boom lowering operation is executed. When the front control function is on, depending on the distance from the excavation target surface of the bucket 23 and the descending speed, the opening degree of the proportional solenoid valve 61b is suppressed by the limit command value output from the front control unit 120, and the hydraulic signal The maximum value of is limited. When the limit value defined by the opening degree of the proportional solenoid valve 61b is exceeded, the hydraulic pressure signal is reduced to the limit value by the proportional solenoid valve 61b in the process of flowing through the pilot line 51b1. As a result, the boom lowering operation is decelerated from the original speed corresponding to the operation amount, and the bucket 23 is prevented from entering below the excavation target surface. The same applies to operations for outputting pressure signals to other pilot lines (operations of arm cloud, arm dump, bucket cloud, and bucket dump).

3-2. When front control is disabled For example, when a boom lowering operation is performed with the operation lever device 51, a signal output valve 51b for a boom lowering command is opened according to the operation amount. When the front control function is in the off state, the opening degree of the proportional solenoid valve 61b does not change depending on the position of the bucket 23, etc., and the hydraulic drive unit 46 of the boom cylinder control valve 41 corresponds to the operation amount of the operation lever device 51. A pressure signal is input to. Thereby, the boom lowering operation is executed simply in response to the lever operation without being affected by the change in the opening degree of the proportional solenoid valve 61b. The same applies to operations for outputting pressure signals to other pilot lines (operations of arm cloud, arm dump, bucket cloud, and bucket dump).

3-3. Processing Procedure of Command Value Control Unit FIG. 9 is a flowchart showing a procedure for determining a command value by the command value control unit. During operation, the command value control unit 130 repeatedly executes the procedure of FIG. 9 (steps S101 to S107) in a predetermined processing cycle (for example, 0.1 s).

Steps S101 → S102
When the procedure of FIG. 9 is started, the command value control unit 130 first inputs the signals of the angle detectors 8a to 8c and the pressure detectors 6a and 6b to the distance calculation unit 133 via the input unit 110 in step S101. In this example, the positional relationship between the excavation target surface S and the airframe will be described as known information. However, as described above, when calculating the positional relationship between the airframe and the excavation target surface S in the earth coordinate system, a positioning device is also used. Signals from 9a and 9b, the wireless device 9c, and the inclination detector 8d are also input.

  In subsequent step S102, the command value calculation unit 130 determines whether or not the limit command value is input from the front control unit 120 in the current cycle by the input determination unit 131. When the limit command value is input, the determination signal indicating the presence of input is received, and when the limit command value is not input, the determination signal indicating the information of no input is input from the input determination unit 131 to the command value determination unit 137. Is output.

Step S102 → S103
When the input determination unit 131 determines that the limit command value is input, the command value control unit 130 moves the procedure from step S102 to step S103. In a situation where the limit command value is input, the distance D between the excavation target surface S and the specific point P is equal to or less than the set distance D0. In step S <b> 103, a determination signal indicating that the limit command value is input is received from the input determination unit 131, and the limit command value from the front control unit 120 is selected as the command value by the command value determination unit 137 and is output to the output unit 170. . In this case, a command signal having a magnitude of the limit command value is output from the output unit 170 and is output to the electromagnetic drive unit of the corresponding proportional solenoid valve. When the procedure of step S103 is completed, the command value control unit 130 once ends the procedure of FIG. 9, starts the next cycle, and executes the process of step S101.

Steps S102 → S104 → S105 → S106
When the input determination unit 131 determines that no limit command value is input, the command value control unit 130 moves the procedure from step S102 to step S104. In step S104, the distance calculation unit 133 calculates the distance D between the excavation target surface S and the specific point P, and the speed calculation unit 135 calculates the operating speed V of the boom cylinder 31. The calculated distance D is input from the distance calculation unit 133 to the distance determination unit 134, and the operation speed V is input from the speed calculation unit 135 to the speed determination unit 136.

  When the procedure of step S104 is completed, the command value control unit 130 moves the procedure to step S105. In step S105, the distance determination unit 134 determines whether the distance D is greater than the set distance D0 read from the set distance storage unit 141. Since the set distance D0 is a positive value and the sign of the distance D is also distinguished as described above, it is determined here whether the specific point P is in the excavation area and is farther from the excavation target surface S than the set distance D0. . The determination result of the distance determination unit 134 is input to the command value determination unit 137 as a determination signal representing the magnitude relationship between D and D0. At the same time, in step S105, the speed determination unit 136 determines whether or not the operation speed V is lower than the set speed V0 read from the set speed storage unit 142. Since the set speed V0 is a positive value and the sign of the operating speed V is also distinguished as described above, it is determined here whether the boom cylinder 31 is not contracted at a speed exceeding the set speed V0. The determination result of the speed determination unit 136 is input to the command value determination unit 137 as a determination signal indicating the magnitude relationship between V and V0.

  As a result of the determination in step S105, when D> D0 and V <V0, the command value control unit 130 moves the procedure to step S106. In step S106, based on the determination signals of the input determination unit 131, the distance determination unit 134, and the speed determination unit 136, the power saving command value read from the power saving command value storage unit 146 is selected as the command value by the command value determination unit 137. And output to the output unit 170. In this case, a command signal having the magnitude of the power saving command value is output from the output unit 170, and each proportional solenoid valve is in a demagnetized state. When the procedure of step S106 is completed, the command value control unit 130 ends the procedure of FIG. 9 once, starts the next cycle, and executes the process of step S101.

Steps S102 → S104 → S105 → S107
When the procedures of steps S102, S104, and S105 are executed and the condition of D> D0 and V <V0 is not satisfied, the command value control unit 130 moves the procedure from step S105 to step S107. In step S107, the standby command value read from the standby command value storage unit 145 is selected as the command value by the command value determination unit 137 based on the determination signals from the input determination unit 131, the distance determination unit 134, and the speed determination unit 136. The data is output to the output unit 170. In this case, a command signal having the magnitude of the standby command value is output from the output unit 170, and each proportional solenoid valve is in a standby state at an intermediate opening. When the procedure of step S107 is completed, the command value control unit 130 once ends the procedure of FIG. 9, starts the next cycle, and executes the process of step S101.

4). Effect 4-1. In this embodiment, when the specific point P is separated from the excavation target surface S by more than the set distance D0 and the boom cylinder 31 is not contracted at a speed exceeding the set speed V0, the pressure reduction and pressure increase A power saving command value command signal is output to the proportional solenoid valves (proportional solenoid valves 61b, 71a, etc.). That is, when the bucket 23 is far from the excavation target surface S and the bucket 23 is not likely to be immediately removed from the excavation area even if the operation state of the front work device 20 is taken into consideration, the command signal of the power saving command value is output to be proportional. Demagnetize the solenoid valve. As described with reference to FIGS. 6 and 7, the power saving command value (i0, i4) is smaller than the minimum command value (i1, i5) in the opening adjustment region. Thereby, compared with the case where the command value of the command signal corresponding to demagnetization is set to the minimum value of the opening adjustment range, the specific point P is more than a certain distance from the excavation target surface S, and the proportional solenoid valve for front control is The exciting current that flows through the proportional solenoid valve in a scene that is not controlled can be suppressed. Therefore, according to this embodiment, power consumption can be suppressed and energy efficiency can be improved.

4-2. In the present embodiment, when the front controller 120 does not generate a limit command value, when a proportional solenoid valve (such as the proportional solenoid valve 61b) is kept waiting for input of the next limit command value, The proportional solenoid valve is set to an intermediate opening by outputting a command signal for the standby command value. Even if a limit command value is input from the front control unit 120 in this state, the movement distance of the spool of the proportional solenoid valve is a distance from the intermediate opening to the maximum opening or the minimum opening at the maximum. . As a result, there is no scene where the spool is driven at a stroke from the position where the proportional solenoid valve is set to the minimum opening to the position where the proportional opening is set to the maximum opening. Therefore, it is possible to suppress a decrease in responsiveness to the operation, and consequently, it is possible to suppress a decrease in the operation accuracy of the front work device 20.

5. Others In the above-described embodiment, the case where the proportional solenoid valve is set to the intermediate opening degree when the limit command value is not generated by the front control unit 120 has been described. However, the setting of the standby command value is directly related to the purpose of setting the command value for demagnetizing the proportional solenoid valves (proportional solenoid valves 61b, 71a, etc.) lower than the minimum value of the opening adjustment range. Absent. Accordingly, the standby command value is not i2, but may be, for example, i1 or i3 in FIG.

  Further, the case where the condition is satisfied in step S105 when D> D0 and V <V0 is set, and the value of the command signal is set to the power saving command value is illustrated. However, the condition regarding the operating speed V (V <V0) may be omitted. That is, when the limit command value is not generated by the front control unit 120, simply if D> D0, the value of the command signal is the power saving command value, and if D ≦ D0, the value of the command signal is the standby command value. You may do it. Even in this case, the value of the command signal can be selected from the limit command value, the power saving command value, and the standby command value, and the merit of simplification of processing can be obtained, and the set speed storage unit 142, the speed calculation unit 135, the speed determination unit 136 may also be omitted.

  In the above embodiment, the case where the expansion / contraction speed of the boom cylinder 31 is calculated as the operation speed V of the hydraulic actuator has been described as an example. However, the expansion / contraction speed of the arm cylinder 32 or the bucket cylinder 33 is set as the operation speed V. It may be used. Of course, a configuration may be adopted in which a plurality of hydraulic actuators 31-33 are selected and their operating speed V is taken into account. Further, the moving speed of the specific point P is calculated from the operating speed V of one or a plurality of hydraulic actuators, the component perpendicular to the excavation target surface S is extracted, and the approach speed of the specific point P to the excavation target surface S in the excavation area. Can be calculated. Instead of simply considering the operating speed V of the hydraulic actuator, it may be considered that this is converted to the approach speed of the specific point P to the excavation target surface S and used as a basis for judgment.

  Note that functional units corresponding to the distance calculation unit 133 and the speed calculation unit 135 may be included in the front control unit 120. In that case, the distance D and the operation speed V calculated by the front control unit 120 may be input to the distance determination unit 134 and the speed determination unit 136 of the command value control unit 130.

  Moreover, although the case where the proportional solenoid valves 61b, 62a, 62b, 63a, 63b for pressure reduction and the proportional solenoid valves 71a, 73a, 73b for pressure increase are provided for front control has been described as an example, all of these are necessary. Not necessarily. If at least one of these (for example, there is a proportional solenoid valve 61b for reducing the hydraulic pressure signal for boom lowering instruction), a kind of front control can be executed.

  Further, the case where the operation speed V of the hydraulic actuator is calculated based on the magnitude of the pressure signal has been described as an example, but the operation of the hydraulic actuator is also performed based on, for example, the rate of change of the signals of the angle detectors 8a to 8c. The speed V can be obtained. For example, the expansion / contraction speed of the boom cylinder 31 can be obtained based on the rate of change of the signal of the angle detector 8a. The operation speed V of the hydraulic actuator can also be obtained using a stroke detector that detects the stroke amount of the hydraulic actuators 31 to 33 and an inclination angle detector that detects the inclination angles of the boom 21, arm 22, and bucket 23.

  Further, a general hydraulic excavator that uses an engine as the prime mover 17 and drives the hydraulic pump 36 and the like by the engine has been described as an example. However, a hybrid hydraulic excavator that drives the hydraulic pump 36 and the like using the engine and the electric motor as a prime mover has been described. In addition, the present invention is applicable. In addition, the present invention can be applied to an electric excavator that drives a hydraulic pump using an electric motor as a prime mover.

8a to 8c ... Angle detector (attitude detector), 10 ... Vehicle body, 20 ... Front working device, 31 ... Boom cylinder (hydraulic actuator), 32 ... Arm cylinder (hydraulic actuator), 33 ... Bucket cylinder (hydraulic actuator), 34 ... Swivel motor (hydraulic actuator), 36 ... hydraulic pump, 37 ... pilot pump, 37a ... pump line, 41-44 ... control valve, 51-54 ... operating lever device, 51a1, 51a2, 51b1, 52a1, 52b1, 53a1 , 53a2, 53b1, 53b2, 54a1, 54b1 ... pilot line, 61b, 62a, 62b, 63a, 63b ... proportional solenoid valve for pressure reduction, 71a, 73a, 73b ... proportional solenoid valve for pressure increase, 100 ... controller unit, 120 ... Front controller 131 ... Force determination unit, 133 ... distance calculation unit, 134 ... distance determination unit, 137 ... command value determination unit, 142 ... set speed storage unit, 145 ... standby command value storage unit, 146 ... power saving command value storage unit, 170 ... output Part, P ... specific point of front working device, S ... distance between specific point and excavation target surface

Claims (1)

A vehicle body, a front working device provided on the vehicle body, a plurality of hydraulic actuators that drive the front working device, a posture detector that detects a posture of the front working device, a hydraulic pump that discharges hydraulic fluid that drives the hydraulic actuator, A plurality of control valves for controlling the flow of hydraulic oil supplied from the hydraulic pump to the corresponding hydraulic actuator, an operation lever device for generating a hydraulic signal instructing the operation of the corresponding hydraulic actuator according to the operation, and the operation lever device A pilot pump that supplies hydraulic oil to the control lever, a plurality of pilot lines that connect the hydraulic drive portions of the control lever device and the corresponding control valve, a plurality of pump lines that connect the hydraulic drive portions of the pilot pump and the control valve, Less of the pilot line The proportional solenoid valve for pressure reduction provided in one, the proportional solenoid valve for pressure increase provided in at least one of the plurality of pump lines, and the proportional solenoid valve based on the detection signal of the attitude detector In a work machine including a controller having a front control unit that calculates a restriction command value that restricts the operation of the front work device,
The controller is
Power-saving command value storage that stores a power-saving command value that is an excitation current set lower than the minimum value of the excitation current applied in the opening adjustment region to the electromagnetic drive unit of the proportional solenoid valve for pressure reduction and pressure increase And
A distance calculation unit that calculates the distance between the specific point of the front work device and the excavation target surface based on the detection signal of the posture detector;
A set distance storage unit storing a preset set distance for the distance between the specific point and the excavation target surface;
A distance determination unit that determines whether a distance between the specific point and the excavation target surface is larger than the set distance;
A speed calculator that calculates the operating speed of the hydraulic actuator based on the pressure of the hydraulic signal of the operating lever device or the detection signal of the attitude detector;
A set speed storage unit that stores a preset set speed for the operating speed of the hydraulic actuator;
A speed determination unit that determines whether or not the operation speed of the hydraulic actuator calculated by the speed calculation unit is greater than the set speed;
When the distance determination unit determines that the distance between the specific point and the excavation target surface is greater than the set distance , and the speed determination unit determines that the operation speed of the hydraulic actuator is less than the set speed , A command value determining unit that determines the power saving command value read from the power saving command value storage unit as a command value for the proportional solenoid valve;
A work machine comprising: an output unit that outputs a command signal to at least one of the pressure reducing and pressure increasing proportional solenoid valves based on the command value determined by the command value determining unit.

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