Work Machine

Abstract

An object of the present invention is to provide a work machine that makes it possible to perform, with a simple configuration, speed control of respective actuators and thrust control of a particular actuator that regenerates the flow of a return fluid, at the time of combined operation to simultaneously drive the particular actuator and another actuator. For this purpose, a controller calculates a target thrust that is a target value of a thrust of the particular actuator on the basis of an input amount of an operation device and an output value of a posture sensor, calculates a target meter-out pressure that is a target value of a meter-out pressure of the particular actuator on the basis of the target thrust and a meter-in pressure of the particular actuator, and calculates a regeneration control valve target opening area that is a target value of an opening area of a regeneration control valve on the basis of the target meter-out pressure and the meter-out pressure of the particular actuator.

Description

TECHNICAL FIELD

The present invention relates to a work machine such as a hydraulic excavator.

BACKGROUND ART

Typically, for example, various hydraulic actuators are provided in a work machine such as a hydraulic excavator, and there is a conventionally widely known control circuit for performing fluid supply/discharge control of such hydraulic actuators, the control circuit being configured to perform, with one spool valve, direction switch control to switch the direction of supply/discharge of a hydraulic working fluid to/from a hydraulic actuator, meter-in opening control to control the flow rate of the hydraulic working fluid supplied from a hydraulic pump to the hydraulic actuator, and meter-out opening control to control the flow rate of the hydraulic working fluid discharged from the hydraulic actuator to a hydraulic working fluid tank. In addition, there is a known control circuit that supplies (regenerates the flow of) a fluid (return fluid) discharged from one hydraulic chamber of a hydraulic actuator directly to the other hydraulic chamber.

In the case of the control circuit that performs, with the one spool valve, the meter-in opening control and meter-out opening control of a hydraulic actuator, the relation between the meter-in side opening area and the meter-out side opening area with respect to the movement position of the spool valve is uniquely determined, undesirably. Therefore, there is a possibility that the relation between the meter-in side opening area and the meter-out side opening area cannot be changed according to various types of work contents such as a single action to drive one hydraulic actuator singly, a combined action to simultaneously drive a plurality of hydraulic actuators, light work, or heavy work, and, when the flow rate of the hydraulic working fluid supplied to an actuator is controlled by the meter-in opening control or when the flow rate of the hydraulic working fluid discharged from the actuator is controlled by the meter-out opening control, one type of opening control interferes with the other type of opening control undesirably, and operability lowers undesirably.

In view of this, there is a conventionally known control circuit that performs fluid supply/discharge control of a hydraulic actuator by using a bridge circuit formed by using four metering valves which are head side and rod side supply valves (head end and rod end supply valves) that control the flow rates of a fluid supplied from a hydraulic pump to the head side hydraulic chamber and the rod side hydraulic chamber of a hydraulic cylinder, respectively, and head side and rod side discharge valves (head end and rod end drain valves) that control the flow rates of the fluid discharged from the head side hydraulic chamber and the rod side hydraulic chamber to a fluid tank, respectively (e.g., Patent Document 1). Since the four metering valves are actuated separately on the basis of a command from a controller in the control circuit, it is possible to easily change the relation between meter-in opening and meter-out opening according to work contents or the like.

In addition, there is also a known control circuit in which an auxiliary valve having a variable resistance function is disposed upstream of a directional control valve that performs, with the one spool valve, the direction switch control, meter-in opening control, and meter-out opening control mentioned before, and hydraulic fluid supply to the directional control valve is performed auxiliarily by the auxiliary valve according to work contents or the like such as a single action or a combined action (e.g., Patent Document 2).

PRIOR ART DOCUMENT

Patent Documents

• Patent Document 1: JP-5214450-B2
• Patent Document 2: JP-3511425-B2

SUMMARY OF THE INVENTION

Problem to be Solved by the Invention

Since the fluid supply/discharge control of one actuator is performed by the four metering valves in the control circuit of Patent Document 1, it is considered that it is possible to realize both speed control of the actuator by the meter-in opening control and thrust control of the actuator by the meter-out opening control. However, since the control circuit requires four drive devices (solenoids in Patent Document 1) for driving four spools (or poppets) included in the four metering valves in addition to the spools, the control circuit has a problem that costs increase due to the complication of the circuit and the increase of the number of parts. In addition, Patent Document 1 does not include a description related to meter-in opening control and meter-out opening control of an actuator to regenerate the flow of a return fluid.

Meanwhile, although the control circuit of Patent Document 2 can control the hydraulic fluid allocation to each actuator or the degrees of priority at the time of a combined action by using the auxiliary valve, meter-in opening control and meter-out opening control of a hydraulic actuator are performed by using one directional control valve as in conventional technologies, and accordingly, the problem that one type of opening control interferes with the other type of opening control undesirably is still left unsolved.

Accordingly, it is not possible to realize both speed control of an actuator by the meter-in opening control and thrust control of the actuator by the meter-out opening control.

The present invention has been made in view of the problems described above, and an object thereof is to provide a work machine that makes it possible to perform, with a simple configuration, speed control of respective actuators and thrust control of a particular actuator that regenerates the flow of a return fluid, at the time of combined operation to simultaneously drive the particular actuator and another actuator.

Means for Solving the Problem

In order to achieve the object described above, the present invention provides a work machine including a machine body, a work implement attached to the machine body, a hydraulic working fluid tank, a variable displacement hydraulic pump that sucks and delivers a hydraulic working fluid from the hydraulic working fluid tank, a regulator that controls a displacement of the hydraulic pump, a plurality of actuators that drive the work implement, a plurality of directional control valves that control a flow of a hydraulic fluid supplied from the hydraulic pump to the plurality of actuators, an operation device that gives an instruction for an action of the plurality of actuators, a regeneration flow path that connects a meter-out flow path connecting a particular directional control valve in the plurality of directional control valves to the hydraulic working fluid tank and a meter-in flow path connecting the particular directional control valve to the hydraulic pump, a regeneration valve that is provided on the regeneration flow path and causes a return fluid of a particular actuator that is one of the plurality of actuators and corresponds to the particular directional control valve to merge with the meter-in flow path from the meter-out flow path, a regeneration control valve that is provided downstream of a point of branch from the regeneration flow path on the meter-out flow path and controls a passing flow rate of the regeneration valve by adjusting a flow rate of the hydraulic fluid returned from the particular actuator to the hydraulic working fluid tank, and a controller that controls the regulator, the plurality of directional control valves, and the regeneration control valve according to an input amount of the operation device. The work machine includes a first pressure sensor that senses a pump pressure that is a delivery pressure of the hydraulic pump, second pressure sensors that sense meter-in pressures and meter-out pressures of the plurality of actuators, and a posture sensor that senses postures and action states of the machine body and the work implement. The plurality of directional control valves are formed by using identical valve bodies and identical housings such that meter-in opening areas become smaller than meter-out opening areas in response to a valve displacement. The controller is configured to calculate an actuator target flow rate that is a target value of a flow rate of the hydraulic fluid supplied from the hydraulic pump to the plurality of actuators on the basis of the input amount of the operation device, calculate an estimated regeneration flow rate that is an estimated value of the passing flow rate of the regeneration valve on the basis of an opening area of the regeneration valve and a meter-in pressure and a meter-out pressure of the particular actuator, calculate a pump target flow rate that is a target value of a delivery flow rate of the hydraulic pump on the basis of the actuator target flow rate and the estimated regeneration flow rate, calculate a target meter-in opening area that is a target value of meter-in opening areas of the plurality of directional control valves on the basis of the actuator target flow rate, the pump pressure, and the meter-in pressure, calculate a target thrust that is a target value of a thrust of the particular actuator on the basis of the input amount of the operation device and an output value of the posture sensor, calculate a target meter-out pressure that is a target value of the meter-out pressure of the particular actuator on the basis of the target thrust and the meter-in pressure of the particular actuator, calculate a regeneration control valve target opening area that is a target value of an opening area of the regeneration control valve on the basis of the target meter-out pressure and the meter-out pressure of the particular actuator, control the regulator according to the pump target flow rate, control the plurality of directional control valves according to the target meter-in opening area, and control the regeneration control valve according to the regeneration control valve target opening area.

According to the thus configured present invention, at the time of combined operation to simultaneously drive the particular actuator that regenerates the flow of the return fluid and the other actuator, the meter-in opening of each directional control valve is adjusted according to the differential pressure across the directional control valve, thereby making it possible to supply the hydraulic fluid at a targeted flow rate to each actuator. In addition, the meter-out opening of the particular directional control valve is adjusted to input a targeted thrust to the particular actuator, thereby making it possible to prevent an excessive movement of an undriven member due to inertia. Then, since the respective directional control valves have a simple configuration formed by using identical valve bodies and identical housings in terms of the meter-in opening areas and the meter-out opening areas, costs can be reduced. This makes it possible to perform, with a simple configuration, speed control of the respective actuators and thrust control of the particular actuator that regenerates the flow of the return fluid, at the time of combined operation to simultaneously drive the particular actuator and the other actuator.

Advantages of the Invention

The work machine according to the present invention makes it possible to perform, with a simple configuration, speed control of a particular actuator that regenerates the flow of a return fluid and another actuator and thrust control of the particular actuator, at the time of combined operation to simultaneously drive the particular actuator and the other actuator.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a side view of a hydraulic excavator according to an embodiment of the present invention.

FIG. 2A is a circuit diagram (1/2) of a hydraulic drive system mounted on the hydraulic excavator depicted in FIG. 1.

FIG. 2B is a circuit diagram (2/2) of the hydraulic drive system mounted on the hydraulic excavator depicted in FIG. 1.

FIG. 3 is a figure depicting opening characteristics of directional control valves depicted in FIG. 2A.

FIG. 4 is a figure depicting opening characteristics of bleed-off valves depicted in FIG. 2A.

FIG. 5 is a functional block diagram of a controller depicted in FIG. 2B.

FIG. 6 is a flowchart depicting a process related to pump flow rate control performed by the controller depicted in FIG. 2B.

FIG. 7 is a flowchart depicting a process related to opening control of boom directional control valves performed by the controller depicted in FIG. 2B.

FIG. 8 is a flowchart depicting a process related to opening control of arm directional control valves performed by the controller depicted in FIG. 2B.

FIG. 9 is a flowchart depicting a process related to opening control of an arm regeneration control valve performed by the controller depicted in FIG. 2B.

FIG. 10 is a flowchart depicting a process related to opening control of bleed-off valves performed by the controller depicted in FIG. 2B.

MODES FOR CARRYING OUT THE INVENTION

Hereinbelow, as an example of a work machine according to an embodiment of the present invention, a hydraulic excavator is explained with reference to the figures. Note that equivalent members in the figures are given identical reference characters, and overlapping explanations are omitted as appropriate.

FIG. 1 is a side view of a hydraulic excavator according to the present embodiment. As depicted in FIG. 1, a hydraulic excavator 901 includes a track structure 201, a swing structure 202 that is arranged swingably on the track structure 201 and included in the machine body, and a work implement 203 that is attached vertically rotatably to the swing structure 202 and performs excavation work of earth and sand and the like. The swing structure 202 is driven by a swing motor 211.

The work implement 203 has a boom 204 attached vertically rotatably to the swing structure 202, an arm 205 attached vertically rotatably to the front end of the boom 204, a bucket 206 attached vertically rotatably to the front end of the arm 205, a boom cylinder 204a as an actuator that drives the boom 204, an arm cylinder 205a as an actuator that drives the arm 205, and a bucket cylinder 206a as an actuator that drives the bucket 206. Inertial measurement units 212, 213, and 214 for sensing the postures and action states of the boom 204, the arm 205, and the bucket 206, respectively, are installed on the work implement 203. Inertial measurement units 215 and 216 for sensing the posture and rotation speed of the swing structure 202 are installed on the swing structure 202. That is, the inertial measurement units 212 to 216 in the present embodiment are included in posture sensors that sense the postures and action states of the swing structure 202 and the work implement 203.

An operation room 207 is provided at a front position on the swing structure 202, and a counter weight 209 for ensuring that the weight balance of the machine body is kept is attached at a rear position on the swing structure 202. A machine room 208 is provided between the operation room 207 and the counter weight 209. The machine room 208 houses an engine (not illustrated), a control valve 210, the swing motor 211, hydraulic pumps 1 to 3 (depicted in FIG. 2A), and the like. The control valve 210 controls the flow of a hydraulic working fluid from the hydraulic pumps to respective actuators.

FIG. 2A and FIG. 2B are circuit diagrams of a hydraulic drive system mounted on the hydraulic excavator 901.

(Configuration)

A hydraulic drive system 902 includes three main hydraulic pumps (e.g., the first hydraulic pump 1, the second hydraulic pump 2, and the third hydraulic pump 3 that include variable displacement hydraulic pumps), a pilot pump 91, and a hydraulic working fluid tank 5 that supplies the fluid to the hydraulic pumps 1 to 3 and the pilot pump 91. The hydraulic pumps 1 to 3 and the pilot pump 91 are driven by the engine (not illustrated).

The tilting angle of the first hydraulic pump 1 is controlled by a regulator provided in association with the first hydraulic pump 1. The regulator of the first hydraulic pump 1 has a flow rate control command pressure port 1a and is driven by a command pressure acting on the flow rate control command pressure port 1a. The tilting angle of the second hydraulic pump 2 is controlled by a regulator provided in association with the second hydraulic pump 2. The regulator of the second hydraulic pump 2 has a flow rate control command pressure port 2a and is driven by a command pressure acting on the flow rate control command pressure port 2a. The tilting angle of the third hydraulic pump 3 is controlled by a regulator provided in association with the third hydraulic pump 3. The regulator of the third hydraulic pump 3 has a flow rate control command pressure port 3a and is driven by a command pressure acting on the flow rate control command pressure port 3a.

A travel-right directional control valve 6, a bucket directional control valve 7, a second arm directional control valve 8, and a first boom directional control valve 9 are connected in parallel on a pump line 40 of the first hydraulic pump 1 via meter-in flow paths 41 and 42, meter-in flow paths 43 and 44, meter-in flow paths 45 and 46, and meter-in flow paths 47 and 48, respectively. In order to prevent reverse flows of the hydraulic fluid to the pump line 40, check valves 21 to 24 are arranged on the meter-in flow paths 41 and 42, the meter-in flow paths 43 and 44, the meter-in flow paths 45 and 46, and the meter-in flow paths 47 and 48, respectively. The travel-right directional control valve 6 controls the flow of the hydraulic fluid supplied from the first hydraulic pump 1 to a travel-right motor that is one of a pair of travel motors for driving the track structure 201 and is not illustrated. The bucket directional control valve 7 controls the flow of the hydraulic fluid supplied from the first hydraulic pump 1 to the bucket cylinder 206a. The second arm directional control valve 8 controls the flow of the hydraulic fluid supplied from the first hydraulic pump 1 to the arm cylinder 205a. The first boom directional control valve 9 controls the flow of the hydraulic fluid supplied from the first hydraulic pump 1 to the boom cylinder 204a. In order to protect the circuit from an excessive pressure increase, the pump line 40 is connected to the hydraulic working fluid tank 5 via a main relief valve 18. In order to discharge an excess delivered fluid of the hydraulic pump 1, the pump line 40 is connected to the hydraulic working fluid tank 5 via a bleed-off valve 35.

A second boom directional control valve 10, a first arm directional control valve 11, a first attachment directional control valve 12, and a travel-left directional control valve 13 are connected in parallel on a pump line 50 of the second hydraulic pump 2 via meter-in flow paths 51 and 52, meter-in flow paths 53 and 54, meter-in flow paths 55 and 56, and meter-in flow paths 57 and 58, respectively. In order to prevent reverse flows of the hydraulic fluid to the pump line 50, check valves 25 to 28 are arranged on the meter-in flow paths 51 and 52, the meter-in flow paths 53 and 54, the meter-in flow paths 55 and 56, and the meter-in flow paths 57 and 58, respectively. The second boom directional control valve 10 controls the flow of the hydraulic fluid supplied from the second hydraulic pump 2 to the boom cylinder 204a. The first arm directional control valve 11 controls the flow of the hydraulic fluid supplied from the second hydraulic pump 2 to the arm cylinder 205a. The first attachment directional control valve 12 controls the flow of the hydraulic fluid supplied from the second hydraulic pump 2 to, for example, a first actuator that drives a first special attachment such as a secondary crusher provided instead of the bucket 206 and is not illustrated. The travel-left directional control valve 13 controls the flow of the hydraulic fluid supplied from the second hydraulic pump 2 to a travel-left motor that is one of the pair of travel motors for driving the track structure 201 and is not illustrated. In order to protect the circuit from an excessive pressure increase, the pump line 50 is connected to the hydraulic working fluid tank 5 via a main relief valve 19. In order to discharge an excess delivered fluid of the hydraulic pump 2, the pump line 50 is connected to the hydraulic working fluid tank 5 via a bleed-off valve 36. In order to cause the delivered fluid of the first hydraulic pump 1 to merge, the pump line 50 is connected to the pump line 40 via a confluence valve 17. A portion of the pump line 50 at which the meter-in flow path 55 and the meter-in flow path 57 are connected is provided with a check valve 32. The check valve 32 prevents the hydraulic fluid that merges with the pump line 50 from the first hydraulic pump 1 via the confluence valve 17 from flowing into the directional control valves 10 to 12 other than the travel-left directional control valve 13. A meter-out side port of the first arm directional control valve 11 is connected to the hydraulic working fluid tank 5 via a meter-out flow path 75. The meter-out flow path 75 is connected to the meter-in flow path 54 via an arm regeneration flow path 76. The arm regeneration flow path 76 is provided with an arm regeneration valve 33 that permits a flow from the meter-out flow path 75 to the meter-in flow path 54. A regeneration control valve and an arm regeneration control valve 34 that control the passing flow rate of the regeneration valve by adjusting the flow rate of the hydraulic fluid returned from the arm cylinder 205a to the hydraulic working fluid tank 5 is installed downstream of a point of branch from the arm regeneration valve 33 on the meter-out flow path 75.

A swing directional control valve 14, a third boom directional control valve 15, and a second attachment directional control valve 16 are connected in parallel on a pump line 60 of the third hydraulic pump 3 via meter-in flow paths 61 and 62, meter-in flow paths 63 and 64, and meter-in flow paths 65 and 66, respectively. In order to prevent reverse flows of the hydraulic fluid to the pump line 60, check valves 29 to 31 are arranged on the meter-in flow paths 61 and 62, the meter-in flow paths 63 and 64, and the meter-in flow paths 65 and 66, respectively. The swing directional control valve 14 controls the flow of the hydraulic fluid supplied from the third hydraulic pump 3 to the swing motor 211. The third boom directional control valve 15 controls the flow of the hydraulic fluid supplied from the third hydraulic pump 3 to the boom cylinder 204a. The second attachment directional control valve 16 is used for controlling the flow of the hydraulic fluid supplied to a second actuator when a second special attachment including the second actuator is attached in addition to the first special attachment or when a second special attachment including two actuators, the first actuator and the second actuator, is attached instead of the first special actuator. In order to protect the circuit from an excessive pressure increase, the pump line 60 is connected to the hydraulic working fluid tank 5 via a main relief valve 20. In order to discharge an excess delivered fluid of the hydraulic pump 3, the pump line 60 is connected to the hydraulic working fluid tank 5 via a bleed-off valve 37.

FIG. 3 depicts opening characteristics of the directional control valves 6 to 16. In FIG. 3, a meter-in opening area increases from zero to its maximum opening area according to a spool displacement. A meter-out opening area also increases similarly from zero to its maximum opening area according to the spool displacement, but is set to values smaller than the values of the meter-in opening area in relation to the spool displacement. This makes it possible to control the drive speed of an actuator by meter-in opening. FIG. 4 depicts opening characteristics of the bleed-off valves 35 to 37. In FIG. 4, a bleed-off valve opening area is its maximum opening area while a maximum operation lever input amount is within the range from zero to a predetermined value, and decreases sharply to zero once the maximum operation lever input amount exceeds the predetermined value. Note that the maximum operation lever input amount mentioned here is the maximum value of each operation lever input amount corresponding to one of a plurality of actuators connected to a pump line connected with a relevant bleed-off valve.

With reference back to FIG. 2A, a pressure sensor 85 that senses the delivery pressure (pump pressure P_Pmp2) of the second hydraulic pump 2 is provided on the pump line 50. Pressure sensors 86 and 87 for sensing the meter-in side pressure (boom meter-in pressure P_MIBm) of the boom cylinder 204a are provided on flow paths 73 and 74 connecting the boom cylinder 204a and the boom directional control valves 9, 10, and 15. Pressure sensors 88 and 89 for sensing the meter-in side pressure (arm meter-in pressure P_MIAm) and meter-out side pressure (arm meter-out pressure P_MoAm) of the arm cylinder 205a are provided on flow paths 71 and 72 connecting the arm cylinder 205a and the arm directional control valves 8 and 11. Output values of the pressure sensors 85 to 89 are inputted to a controller 94.

In FIG. 2B, a delivery port of the pilot pump 91 is connected to the hydraulic working fluid tank 5 via a pilot relief valve 92 for pilot primary pressure generation, and also is connected to one input port of each of solenoid valves 93a to 93g built in a solenoid valve unit 93 via a flow path 80. The other input port of each of the solenoid valves 93a to 93f is connected to the hydraulic working fluid tank 5 via a flow path 81. Each of the solenoid valves 93a to 93g reduces the pilot primary pressure in accordance with a command signal from the controller 94, and outputs the reduced pilot primary pressure as a command pressure.

An output port of the solenoid valve 93a is connected to the flow rate control command pressure port 2a of the regulator of the second hydraulic pump 2. Output ports of the solenoid valves 93b and 93c are connected to pilot ports 10a and 10b of the second boom directional control valve 10. Output ports of the solenoid valves 93d and 93e are connected to pilot ports 11a and 11b of the first arm directional control valve 11. An output port of the solenoid valve 93f is connected to a command pressure port 36a of the bleed-off valve 36. An output port of the solenoid valve 93g is connected to a command pressure port 34a of the regeneration control valve 34.

Note that, for simplification of explanation, illustrations of solenoid valves for the flow rate control command pressure ports 1a and 3a of the regulators of the first hydraulic pump 1 and the third hydraulic pump 3, a solenoid valve for the travel-right directional control valve 6, a solenoid valve for the bucket directional control valve 7, a solenoid valve for the second arm directional control valve 8, a solenoid valve for the first boom directional control valve 9, a solenoid valve for the first attachment directional control valve 12, a solenoid valve for the travel-left directional control valve 13, a solenoid valve for the swing directional control valve 14, a solenoid valve for the third boom directional control valve 15, a solenoid valve for the second attachment directional control valve 16, and solenoid valves for the bleed-off valves 35 and 37 are omitted.

The hydraulic drive system 902 includes a boom operation lever 95a capable of switch operation of the first boom directional control valve 9, the second boom directional control valve 10, and the third boom directional control valve 15, and an arm operation lever 95b capable of switch operation of the first arm directional control valve 11 and the second arm directional control valve 8. Note that, for simplification of explanation, illustrations of a travel-right operation lever for switch operation of the travel-right directional control valve 6, a bucket operation lever for switch operation of the bucket directional control valve 7, a first attachment operation lever for switch operation of the first attachment directional control valve 12, a travel-left operation lever for switch operation of the travel-left directional control valve 13, a swing operation lever for switch operation of the swing directional control valve 14, and a second attachment operation lever for switch operation of the second attachment directional control valve 16 are omitted.

The hydraulic drive system 902 includes the controller 94. According to input amounts of the operation levers 95a and 95b, output values of the inertial measurement units 212 to 216, and output values of the pressure sensors 85 to 89, the controller 94 outputs a command signal to the solenoid valves 93a to 93g (including solenoid valves which are not illustrated) that the solenoid valve unit 93 has.

FIG. 5 is a functional block diagram of the controller 94. In FIG. 5, the controller 94 has a boom target flow rate computing section 94a, an arm target flow rate computing section 94b, an arm estimated regeneration flow rate computing section 94c, an arm corrected target flow rate computing section 94d, a bleed-off valve target opening computing section 94e, an estimated bleed-off flow rate computing section 94f, a pump target flow rate computing section 94g, a pump control command output section 94h, a pressure state assessing section 94i, a boom directional control valve target meter-in opening computing section 94j, a boom directional control valve control command output section 94k, an arm directional control valve target meter-in opening computing section 941, an arm directional control valve control command output section 94m, a required torque computing section 94n, a gravity torque computing section 940, an inertia torque computing section 94p, a target torque computing section 94q, a target thrust computing section 94r, an arm target meter-out pressure computing section 94s, an arm regeneration control valve target opening computing section 94t, an arm regeneration control valve control command output section 94u, and a bleed-off valve control command output section 94v.

The boom target flow rate computing section 94a calculates a target value (boom target flow rate QTgtBm) of the flow rate (boom flow rate) of the hydraulic fluid supplied to the boom cylinder 204a on the basis of an operation lever input amount. Specifically, the boom target flow rate computing section 94a calculates the boom target flow rate Q_TgtBm according to the operation lever input amount in accordance with preset boom flow rate characteristics in relation to operation lever input amounts. The arm target flow rate computing section 94b calculates a target value (arm target flow rate Q_tgtAm) of the flow rate (arm flow rate) of the hydraulic fluid supplied to the arm cylinder 205a on the basis of the operation lever input amount. Specifically, the arm target flow rate computing section 94b calculates the arm target flow rate Q_Tgtam according to the operation lever input amount in accordance with preset arm flow rate characteristics in relation to operation lever input amounts.

The arm estimated regeneration flow rate computing section 94c calculates an arm estimated regeneration flow rate Q_EstRegAm on the basis of the arm meter-in pressure P_MIAm and arm meter-out pressure P_MOAm that are obtained from output values of the pressure sensors 88 and 89, and the opening area of the arm regeneration valve 33. The arm corrected target flow rate computing section 94d calculates an arm corrected target flow rate Q_ModigtAm on the basis of the arm target flow rate Q_TgtAm calculated by the arm target flow rate computing section 94b and the arm estimated regeneration flow rate Q_EstRegAm Calculated by the arm estimated regeneration flow rate computing section 94c.

The bleed-off valve target opening computing section 94e calculates a target opening area of the bleed-off valves 35 to 37 on the basis of the operation lever input amount. Specifically, the bleed-off valve target opening computing section 94e calculates the bleed-off valve target opening area according to the operation lever input amount in accordance with preset bleed-off valve opening area characteristics in relation to operation lever input amounts. The estimated bleed-off flow rate computing section 94f calculates an estimated bleed-off flow rate Q_EstBO on the basis of a bleed-off valve target opening area A_TgtBo calculated by the bleed-off valve target opening computing section 94e and the pump pressure P_Pmp2 obtained from an output value of the pressure sensor 85.

The pump target flow rate computing section 94g calculates a pump target flow rate Q_TgtPmp on the basis of the boom target flow rate Q_TgtBm calculated by the boom target flow rate computing section 94a, the arm target flow rate Q_TgtAm calculated by the arm target flow rate computing section 94b, and the estimated bleed-off flow rate Q_EstBo calculated by the estimated bleed-off flow rate computing section 94f. The pump control command output section 94h outputs, to the solenoid valve 93a, a command signal (pump flow rate control command signal) according to the pump target flow rate Q_TgtPmp calculated by the pump target flow rate computing section 94g, in accordance with preset solenoid valve command signal characteristics in relation to pump flow rates.

The pressure state assessing section 94i assesses whether or not a differential pressure across the directional control valve of each actuator is lower than a predetermined threshold on the basis of an output value of a pressure sensor provided on the corresponding actuator line, and outputs assessment results to the boom directional control valve target meter-in opening computing section 94j. The boom directional control valve target meter-in opening computing section 94j calculates a target meter-in opening area A_TgtMIBm Of the boom directional control valves 9, 10, and 15 on the basis of the boom target flow rate calculated by the boom target flow rate computing section 94a, the pump pressure obtained from the output value of the pressure sensor 85, the boom meter-in pressure obtained from an output value of the pressure sensor 86 (87), and the assessment results outputted from the pressure state assessing section 941. The boom directional control valve control command output section 94k outputs, to the solenoid valve 93b (93c), a command signal (boom directional control valve control command signal) according to the target meter-in opening area A_TgtMIBm calculated by the boom directional control valve target meter-in opening computing section 94j, in accordance with preset solenoid valve command signal characteristics in relation to meter-in opening areas.

The arm directional control valve target meter-in opening computing section 941 calculates a target meter-in opening area A_TgtMIAm of the arm directional control valves 8 and 11 on the basis of the arm target flow rate calculated by the arm target flow rate computing section 94b, the pump pressure obtained from the output value of the pressure sensor 85, the arm meter-in pressure obtained from an output value of the pressure sensor 88 (89), and the assessment results outputted from the pressure state assessing section 941. The arm directional control valve control command output section 94m outputs, to the solenoid valve 93d (93e), a command signal (arm directional control valve control command signal) according to the target meter-in opening area A_TgtMIAm Calculated by the arm directional control valve target meter-in opening computing section 941, in accordance with preset solenoid valve command signal characteristics in relation to meter-in opening areas.

The required torque computing section 94n calculates a required torque T_regAm of the arm 205 according to an arm operation lever input amount in accordance with preset arm required torque characteristics in relation to arm operation lever input amounts. The gravity torque computing section 940 calculates, as a gravity torque T_Gravity, a gravity component of an arm moment on the basis of output values of the inertial measurement units 212 to 216 and machine body specification values. The inertia torque computing section 94p calculates, as an inertia torque T_Inertia, an inertia component of the arm moment on the basis of the gravity torque T_Gravity calculated by the gravity torque computing section 940 and the output values of the inertial measurement units 212 to 216. The target torque computing section 94q calculates a target torque T_TgtAm of the arm 205 on the basis of the required torque calculated by the required torque computing section 94n, the gravity torque T_Gravity calculated by the gravity torque computing section 940, and the inertia torque T_Inertia calculated by the inertia torque computing section 94p. The target thrust computing section 94r calculates a target thrust F_Tgtam of the arm cylinder 205a on the basis of the target torque T_TgtAm calculated by the target torque computing section 94q, the output values of the inertial measurement units 212 to 216, and the machine body specification values.

The arm target meter-out pressure computing section 94s calculates an arm target meter-out pressure P_MOTgtAm on the basis of the target thrust F_Tgtam of the arm cylinder 205a calculated by the target thrust computing section 94r and the arm meter-in pressure P_MIAm obtained from the output value of the pressure sensor 88 (89). The arm regeneration control valve target opening computing section 94t calculates a target opening area A_TgtMOAm of the arm regeneration control valve 34 on the basis of the arm target meter-out pressure P_MOTgtAm Calculated by the arm target meter-out pressure computing section 94s and the arm meter-out pressure P_MoAm obtained from the output value of the pressure sensor 88 (89). The arm regeneration control valve control command output section 94u outputs, to the solenoid valve 93g, a command signal (arm regeneration control valve control command signal) according to the target opening area A_TgtMOAm of the arm regeneration control valve 34 calculated by the arm regeneration control valve target opening computing section 94t, in accordance with preset command electric signal characteristics of solenoid valves in relation to opening areas of the arm regeneration control valve.

The bleed-off valve control command output section 94v outputs, to the solenoid valve 93f, a command signal (bleed-off valve control command signal) according to the target opening area A_TgtBo calculated by the bleed-off valve target opening computing section 94e, in accordance with preset solenoid valve command signal characteristics in relation to opening areas of the bleed-off valves 35 to 37.

FIG. 6 is a flowchart depicting a process related to pump flow rate control performed by the controller 94. Hereinbelow, only a process related to flow rate control of the second hydraulic pump 2 is explained. Note that, since processes related to flow rate control of the other hydraulic pumps 1 and 3 are similar to this, explanations thereof are omitted.

First, the controller 94 assesses whether or not operation lever input is absent (Step S101). Operation lever input mentioned here is operation lever input corresponding to the actuators 204a and 205a connected to the pump line 60 of the second hydraulic pump 2. When it is assessed at Step S101 that operation lever input is absent (YES), the procedure is ended.

When it is assessed at Step S101 that operation lever input is present (NO), the boom target flow rate computing section 94a calculates the boom target flow rate Q_TgtBm according to the operation lever input amount in accordance with preset boom target flow rate characteristics in relation to operation lever input amounts (Step S102A).

In parallel with Step S102A, the arm target flow rate computing section 94b calculates the arm target flow rate Q_TgtAm according to the operation lever input amount in accordance with preset arm target flow rate characteristics in relation to operation lever input amounts (Step S102B). Note that, although an illustration is omitted, target flow rates are also calculated similarly for other actuators connected to the pump line 50 of the second hydraulic pump 2.

Subsequently to Step S102B, the arm estimated regeneration flow rate computing section 94c calculates the arm estimated regeneration flow rate Q_EstRegAm on the basis of the arm meter-in pressure P_MIAm and arm meter-out pressure P_MOAm that are obtained from output values of the pressure sensors 88 and 89, and the opening area of the arm regeneration valve 33 (Step S103).

Subsequently to Step S103, the arm corrected target flow rate computing section 94d calculates the arm corrected target flow rate Q_ModigtAm in accordance with Formula 1 using the arm target flow rate Q_Tgtam calculated by the arm target flow rate computing section 94b and the arm estimated regeneration flow rate Q_EstRegAm calculated by the arm estimated regeneration flow rate computing section 94c (Step S104).

$\begin{array}{cc}\left[\mathrm{Math}.1\right]& \\ Q_{\mathrm{ModiTgtAm}}=Q_{\mathrm{TgtAm}}-Q_{\mathrm{EstRegAm}}& \mathrm{Formula}1\end{array}$

In parallel with Step S102A or Steps S102B, S103, and S104, the estimated bleed-off flow rate computing section 94f calculates the estimated bleed-off flow rate Q_EstBo in accordance with Formula 2 using the target opening area A_TgtBO of the bleed-off valve 36 calculated by the bleed-off valve target opening computing section 94e and the pump pressure P_Pmp2 obtained from the output value of the pressure sensor 85 (Step S105).

$\begin{array}{cc}\left[\mathrm{Math}.2\right]& \\ Q_{\mathrm{EstBO}}=\mathrm{Cd}\times A_{\mathrm{TgtBO}}\text{?}\left(2\left(P_{\mathrm{Pmp}2}-P_{\mathrm{Tank}}\right)/\rho \right)& \mathrm{Formula}2\end{array}$ $\text{?}\text{indicates text missing or illegible when filed}$

Here, Cd is a flow rate coefficient, Prank is a tank pressure, and ρ is a hydraulic working fluid density.

Subsequently to Steps S102A, S104, and S105, the pump target flow rate computing section 94g calculates the pump target flow rate Q_TgtPmp in accordance with Formula 3 using the boom target flow rate Q_TgtBm, the arm corrected target flow rate Q_ModiTgtAm, and the estimated bleed-off flow rate Q_EstBo (Step S106).

$\begin{array}{cc}\left[\mathrm{Math}.3\right]& \\ Q_{\mathrm{TgtPmp}}=Q_{\mathrm{TgtBm}}+Q_{\mathrm{ModiTgtAm}}+\dots +Q_{\mathrm{EstBO}}& \mathrm{Formula}3\end{array}$

Subsequently to Step S106, the pump control command output section 94h outputs, to the solenoid valve 93a for pump flow rate control of the second hydraulic pump 2, a command signal (pump flow rate control command signal) according to the pump target flow rate Q_Tgtemp Calculated by the pump target flow rate computing section 94g, in accordance with preset solenoid valve command signal characteristics in relation to pump flow rates (Step S107).

Subsequently to Step S107, the solenoid valve 93a for pump flow rate control of the second hydraulic pump 2 is caused to generate a command pressure (Step S108), the tilting of the second hydraulic pump 2 is changed in accordance with the command pressure (Step S109), and the procedure ends.

FIG. 7 is a flowchart depicting a process related to opening control of the boom directional control valves 9, 10, and 15 performed by the controller 94. Hereinbelow, only a process related to opening control of the second boom directional control valve 10 is explained. Since processes related to opening control of the other boom directional control valves 9 and 15 are similar to this, explanations thereof are omitted.

First, the controller 94 assesses whether or not boom operation lever input is absent (Step S201). When it is assessed at Step S201 that boom operation lever input is absent (YES), the procedure is ended.

When it is assessed at Step S201 that boom operation lever input is present (NO), the boom target flow rate computing section 94a calculates the boom target flow rate Q_TgtBm according to the boom operation lever input amount in accordance with preset boom target flow rate characteristics in relation to boom operation lever input amounts (Step S202).

Subsequently to Step S202, the pressure state assessing section 94i determines whether or not a differential pressure between the pump pressure P_Pmp2 obtained from an output value of the pressure sensor 85 and the boom meter-in pressure P_MIBm obtained from an output value of the pressure sensor 86 (87) (the differential pressure across the second boom directional control valve 10) is lower than a threshold x (Step S203). For example, the threshold x is set to a minimum value of the differential pressure across the directional control valve at which flow rate control precision can be ensured.

When it is assessed at Step S203 that the differential pressure (P_Pmp2-P_MIBm) is equal to or greater than the threshold a (NO), the boom directional control valve target meter-in opening computing section 94j calculates the target meter-in opening area A_TgtMIBm of the second boom directional control valve 10 in accordance with Formula 4 using the boom target flow rate Q_TgtBm calculated by the boom target flow rate computing section 94a, the pump pressure P_pmp2 of the second hydraulic pump 2 obtained from the output value of the pressure sensor 85, and the boom meter-in pressure P_MIBm obtained from the output value of the pressure sensor 86 (87) (Step S204).

$\begin{array}{cc}\left[\mathrm{Math}.4\right]& \\ A_{\mathrm{TgtMIBm}}=Q_{\mathrm{TgtBm}}/\left(\mathrm{Cd}\times \text{?}\left(2\left(P_{\mathrm{Pmp}2}-P_{\mathrm{MIBm}}\right)/\rho \right)\right)& \mathrm{Formula}4\end{array}$ $\text{?}\text{indicates text missing or illegible when filed}$

Here, Cd is a flow rate coefficient, and ρ is a hydraulic working fluid density.

When it is assessed at Step S203 that the differential pressure (P_Pmp2-P_MIBm) is lower than the threshold a (YES), the boom directional control valve target meter-in opening computing section 94j calculates the target meter-in opening area A_TgtMIBm, as with Step S204, using the threshold a instead of the differential pressure (P_Pmp2-P_MIBm) (Step S205).

Subsequently to Step S204 or Step S205, the boom directional control valve control command output section 94k outputs, to the solenoid valve 93b (93c) for the second boom directional control valve 10, a command signal (boom directional control valve control command signal) according to the target meter-in opening area A_TgtMIBm calculated by the boom directional control valve target meter-in opening computing section 94j, in accordance with preset solenoid valve command signal characteristics in relation to meter-in opening areas of the second boom directional control valve 10 (Step S206).

Subsequently to Step S206, the solenoid valve 93b (93c) for the second boom directional control valve 10 is caused to generate a command pressure (Step S207), the second boom directional control valve 10 is caused to open in accordance with the command pressure (Step S208), and the procedure ends.

FIG. 8 is a flowchart depicting a process related to opening control of the arm directional control valves 8 and 11 performed by the controller 94. Hereinbelow, only a process related to opening control of the first arm directional control valve 11 is explained. Since a process related to opening control of the second arm directional control valve 8 is similar to this, an explanation thereof is omitted. First, the controller 94 assesses whether or not arm operation lever input is absent (Step S301). When it is assessed at Step S301 that arm operation lever input is absent (YES), the procedure is ended.

When it is assessed at Step S301 that arm operation lever input is present (NO), the arm target flow rate computing section 94b calculates the arm target flow rate Q_TgtAm according to the arm operation lever input amount in accordance with preset arm target flow rate characteristics in relation to arm operation lever input amounts (Step S302).

Subsequently to Step S302, the pressure state assessing section 94i determines whether or not a differential pressure between the pump pressure P_Pmp2 obtained from an output value of the pressure sensor 85 and the arm meter-in pressure P_MIAm obtained from an output value of the pressure sensor 88 (89) (the differential pressure across the first arm directional control valve 11) is lower than the threshold x (Step S303).

When it is assessed at Step S303 that the differential pressure (P_Pmp2-P_MIAm) is equal to or greater than the threshold a (NO), the arm directional control valve target meter-in opening computing section 941 calculates the target meter-in opening area A_TgtMIAm of the first arm directional control valve 11 in accordance with Formula 5 using the arm target flow rate Q_TgtAm calculated by the arm target flow rate computing section 94b, the pump pressure P_Pmp2 of the second hydraulic pump 2 obtained from the output value of the pressure sensor 85, and the arm meter-in pressure P_MIAm obtained from the output value of the pressure sensor 88 (89) (Step S304).

$\begin{array}{cc}\left[\mathrm{Math}.5\right]& \\ A_{\mathrm{TgtMIAm}}=Q_{\mathrm{TgtAm}}/\left(\mathrm{Cd}\times \text{?}\left(2\left(P_{\mathrm{Pmp}2}-P_{\mathrm{MIAm}}\right)/\rho \right)\right)& \mathrm{Formula}5\end{array}$ $\text{?}\text{indicates text missing or illegible when filed}$

Here, Cd is a flow rate coefficient, and ρ is a hydraulic working fluid density.

When it is assessed at Step S303 that the differential pressure (P_Pmp2-P_MIAm) is lower than the threshold a (YES), the arm directional control valve target meter-in opening computing section 941 calculates the target meter-in opening area A_TgtMIAm, as with Step S304, using the threshold a instead of the differential pressure (P_Pmp2-P_MIAm) (Step S305).

Subsequently to Step S304 or Step S305, the arm directional control valve control command output section 94m outputs, to the solenoid valve 93d (93e) for the first arm directional control valve 11, a command signal (arm directional control valve control command signal) according to the target meter-in opening area A_TgtMIAm Calculated by the arm directional control valve target meter-in opening computing section 941, in accordance with preset solenoid valve command signal characteristics in relation to meter-in opening areas of the first arm directional control valve 11 (Step S306).

Subsequently to Step S306, the solenoid valve 93d (93e) for the first arm directional control valve 11 is caused to generate a command pressure (Step S307), the first arm directional control valve 11 is caused to open in accordance with the command pressure (Step S308), and the procedure ends. FIG. 9 is a flowchart depicting a process related to opening control of the arm regeneration control valve 34 performed by the controller 94.

First, the controller 94 assesses whether or not arm operation lever input is absent (Step S401). When it is assessed at Step S401 that arm operation lever input is absent (YES), the procedure is ended.

When it is assessed at Step S401 that arm operation lever input is present (NO), the required torque computing section 94n calculates an arm required torque T_ReqAm according to the arm operation lever input amount in accordance with preset arm required torque characteristics in relation to arm operation amount lever input amounts (Step S402).

In parallel with Step S402, the gravity torque computing section 940 calculates, as the gravity torque T_Gravity, the gravity component of an arm moment on the basis of output values of the inertial measurement units 212 to 216 and machine body specification values (mainly, dimensions of the structure, etc.) (Step S403).

Subsequently to Step S403, the inertia torque computing section 94p calculates, as the inertia torque T_Inertia, the inertia component of the arm moment on the basis of the gravity torque T_Gravity calculated by the gravity torque computing section 940 and the output values of the inertial measurement units 212 to 216 (Step S404).

Subsequently to Steps S402 and S404, the target torque computing section 94q calculates an arm target torque T_TgtAm in accordance with Formula 6 using the arm required torque T_ReqAm calculated by the required torque computing section 94n, the gravity torque T_Gravity calculated by the gravity torque computing section 940, and the inertia torque T_Inertia calculated by the inertia torque computing section 94p (Step S405).

$\begin{array}{cc}\left[\mathrm{Math}.6\right]& \\ T_{\mathrm{TgtAm}}=T_{\mathrm{ReqAm}}-T_{\mathrm{Gravity}}-T_{\mathrm{Inertia}}& \mathrm{Formula}6\end{array}$

Here, a torque in a rotation direction that is the same as the direction of the arm required torque T_RegAm is defined as a positive torque.

Subsequently to Step S405, the target thrust computing section 94r calculates the target thrust F_TgtAm Of the arm cylinder 205a on the basis of the arm target torque T_TgtAm calculated by the target torque computing section 94q, the output values of the inertial measurement units 212 to 216, and machine body specification values (Step S406).

Subsequently to Step S406, the arm target meter-out pressure computing section 94s calculates the arm target meter-out pressure P_MOTgtAm in accordance with Formula 7 using the target thrust F_TgtAm calculated by the target thrust computing section 94r and the arm meter-in pressure P_MIAm obtained from an output value of the pressure sensor 88 (89) (Step S407).

$\begin{array}{cc}\left[\mathrm{Math}.7\right]& \\ P_{\mathrm{TgtMOAm}}=\left(S_{\mathrm{MIAm}}\times P_{\mathrm{MIAm}}-F_{\mathrm{TgtAm}}\right)/S_{\mathrm{MOAm}}& \mathrm{Formula}7\end{array}$

Here, S_MIAm is the meter-in side pressure receiving area of the arm cylinder 205a, and S_MOAm is the meter-out side pressure receiving area of the arm cylinder 205a.

Subsequently to Step S407, the arm regeneration control valve target opening computing section 94t calculates the target opening area A_TgtMOAm of the arm regeneration control valve 34 such that a difference between the arm target meter-out pressure P_TgtMOAm Calculated by the arm target meter-out pressure computing section 94s and the arm meter-out pressure P_MOAm Obtained from the output value of the pressure sensor 89 (88) decreases (Step S408).

Subsequently to Step S408, the arm regeneration control valve control command output section 94u outputs, to the solenoid valve 93g for the arm regeneration control valve 34, a command signal (arm regeneration control valve control command signal) according to the target opening area A_TgtMOAm calculated by the arm regeneration control valve target opening computing section 94t, in accordance with preset solenoid valve command signal characteristics in relation to opening areas of the arm regeneration control valve 34 (Step S409).

Subsequently to Step S409, the solenoid valve 93g is caused to generate a command pressure of the arm regeneration control valve 34 (Step S410), the arm regeneration control valve 34 is caused to open in accordance with the command pressure (Step S411), and the procedure ends.

FIG. 10 is a flowchart depicting a process related to opening control of the bleed-off valves 35 to 37 performed by the controller 94. Hereinbelow, only a process related to opening control of the bleed-off valve 36 connected to the pump line 50 of the second hydraulic pump 2 is explained. Since processes related to opening control of the other bleed-off valves are similar to this, explanations thereof are omitted.

First, the controller 94 assesses whether or not operation lever input is absent (Step S501). Operation lever input mentioned here is operation lever input corresponding to the actuators 204a and 205a connected to the pump line 50 of the second hydraulic pump 2. When it is assessed at Step S501 that operation lever input is absent (YES), the procedure is ended.

When it is assessed at Step S501 that operation lever input is present (NO), the bleed-off valve target opening computing section 94e calculates the target opening area A_TgtBO of the bleed-off valve 36 according to the maximum operation lever input amount in accordance with the bleed-off valve opening characteristics depicted in FIG. 4 (Step S502). Note that the maximum operation lever input amount mentioned here is the maximum value of each operation lever input amount corresponding to the actuators 204a and 205a connected to the pump line 50 of the second hydraulic pump 2.

Subsequently to Step S502, the bleed-off valve control command output section 94v outputs, to the solenoid valve 93f for the bleed-off valve 36, a command signal (bleed-off valve control command signal) according to the target opening area A_TgtBo of the bleed-off valve 36 in accordance with preset solenoid valve command signal characteristics in relation to opening areas of the bleed-off valve 36 (Step S503).

Subsequently to Step S503, the solenoid valve 93f is caused to generate a command pressure of the bleed-off valve 36 (Step S504), the bleed-off valve 36 is caused to open in accordance with the command pressure (Step S505), and the procedure ends.

(Actions)

As examples of actions of the hydraulic drive system 902, actions of the second hydraulic pump 2, the second boom directional control valve 10, the first arm directional control valve 11, the arm regeneration control valve 34, and the bleed-off valve 36 in a case where combined operation to simultaneously drive the boom cylinder 204a and the arm cylinder 205a is performed are explained.

“Second Hydraulic Pump”

The controller 94 calculates the pump target flow rate Q_TgtPmp Of the second hydraulic pump 2 on the basis of input amounts of the boom operation lever 95a and the arm operation lever 95b, and outputs, to the solenoid valve 93a, a command signal (pump flow rate control command signal) according to the pump target flow rate Q_TgtPmp. The solenoid valve 93a generates a command pressure according to the pump flow rate control command signal and drives the delivery flow rate of the second hydraulic pump 2.

“Second Boom Directional Control Valve”

The controller 94 calculates the target meter-in opening area A_TgtMIBm on the basis of the boom target flow rate Q_TgtBm calculated on the basis of the input amount of the boom operation lever 95a, the pump pressure P_pmp2 sensed by the pressure sensor 85, and the boom meter-in pressure P_MIBm sensed by the pressure sensor 86 (87), and outputs, to the solenoid valve 93b (93c), a command signal (boom directional control valve control command signal) according to the target meter-in opening area A_TgtMIBm. The solenoid valve 93b (93c) generates a command pressure according to the boom directional control valve control command signal and controls the meter-in opening area of the second boom directional control valve 10.

“First Arm Directional Control Valve”

The controller 94 calculates the target meter-in opening area A_TgtMIAm on the basis of the arm target flow rate Q_TgtAm calculated on the basis of the input amount of the arm operation lever 95b, the pump pressure P_Pmp2 sensed by the pressure sensor 85, and the arm meter-in pressure P_MIAm sensed by the pressure sensor 88 (89), and outputs, to the solenoid valve 93d (93e), a command signal (arm directional control valve control command signal) according to the target meter-in opening area A_TgtMIAm. The solenoid valve 93d (93e) generates a command pressure according to the arm directional control valve control command signal and controls the meter-in opening area of the first arm directional control valve 11.

“Arm Regeneration Control Valve” The controller 94 calculates the target opening area A_TgtMOAm Of the arm regeneration control valve 34 on the basis of the target torque T_TgtAm calculated from the input amount of the arm operation lever 95b, the gravity torque T_Gravity, and the inertia torque T_Inertia of the machine body, and the arm meter-in pressure P_MIAm and the arm meter-out pressure P_MOAm sensed by the pressure sensors 88 and 89, and outputs, to the solenoid valve 93g, a command signal (arm regeneration control valve control command signal) according to the target opening area A_TgtMOAm. The solenoid valve 93g generates a command pressure according to the arm regeneration control valve control command signal and controls the opening area of the arm regeneration control valve 34.

“Bleed-Off Valve”

The controller 94 calculates the target opening area A_TgtBo of the bleed-off valve 36 on the basis of the input amounts of the boom operation lever 95a and the arm operation lever 95b, and outputs, to the solenoid valve 93f, a command signal (bleed-off valve control command signal) according to the target opening area A_TgtBo. The solenoid valve 93f generates a command pressure according to the bleed-off valve control command signal and controls the opening area of the bleed-off valve 36.

SUMMARY

In the present embodiment, the work machine 901 includes the machine body 202, the work implement 203 attached to the machine body 202, the hydraulic working fluid tank 5, the variable displacement hydraulic pump 2 that sucks and delivers the hydraulic working fluid from the hydraulic working fluid tank 5, the regulator 2a that controls the displacement of the hydraulic pump 2, the plurality of actuators 204a and 205a that drive the work implement 203, the plurality of directional control valves 10 and 11 that control the flows of the hydraulic fluid supplied from the hydraulic pump 2 to the plurality of actuators 204a and 205a, the operation devices 95a and 95b that give instructions for actions of the plurality of actuators 204a and 205a, the regeneration flow path 76 that connects the meter-out flow path 75 connecting the particular directional control valve 11 in the plurality of directional control valves 10 and 11 to the hydraulic working fluid tank 5 and the meter-in flow path 54 connecting the particular directional control valve 11 to the hydraulic pump, the regeneration valve 33 that is provided on the regeneration flow path 76 and causes a return fluid of the particular actuator 205a that is one of the plurality of actuators 204a and 205a and corresponds to the particular directional control valve 11 to merge with the meter-in flow path 54 from the meter-out flow path 75, the regeneration control valve 34 that is provided downstream of the point of branch from the regeneration flow path 76 on the meter-out flow path 75 and controls the passing flow rate of the regeneration valve 33 by adjusting the flow rate of the hydraulic fluid returned from the particular actuator 205a to the hydraulic working fluid tank 5, and the controller 94 that controls the regulator 2a, the plurality of directional control valves 10 and 11, and the regeneration control valve 34 according to input amounts of the operation devices 95a and 95b. The work machine 901 includes the first pressure sensor 85 that senses a pump pressure that is the delivery pressure of the hydraulic pump 2, the second pressure sensors 86 to 89 that sense the meter-in pressures P_MIBm and P_MIAm and meter-out pressures P_MOBm and P_MOAm of the plurality of actuators 204a and 205a, and the posture sensors 212 to 216 that sense the postures and action states of the machine body 202 and the work implement 203. The plurality of directional control valves 10 and 11 are formed by using identical valve bodies and identical housings such that meter-in opening areas become smaller than meter-out opening areas in response to a valve displacement. The controller 94 is configured to calculate the actuator target flow rates Q_TgtBm and Q_TgtAm that are target values of the flow rates of the hydraulic fluid supplied from the hydraulic pump 2 to the plurality of actuators 204a and 205a on the basis of the input amounts of the operation devices 95a and 95b, calculate the estimated regeneration flow rate Q_EstRegAm that is an estimated value of the passing flow rate of the regeneration valve 33 on the basis of the opening area of the regeneration valve 33 and the meter-in pressure P_MIAm and meter-out pressure P_MOAm Of the particular actuator 205a, calculate the pump target flow rate Q_Tgtpmp that is a target value of the delivery flow rate of the hydraulic pump 2 on the basis of the actuator target flow rates Q_TgtBm and Q_TgtAm and the estimated regeneration flow rate Q_EstRegAm, calculate the target meter-in opening areas A_TgtMIBm and A_TgtMIAm that are target values of the meter-in opening areas of the plurality of directional control valves 10 and 11 on the basis of the actuator target flow rates Q_TgtBm and Q_TgtAm, the pump pressure P_Pmp2, and the meter-in pressures P_MIBm and P_MIAm, calculate the target thrust F_TgtAm that is a target value of the thrust of the particular actuator 205a on the basis of the input amount of the operation device 95b and output values of the posture sensors 212 to 216, calculate the target meter-out pressure P_MOTgtAm that is a target value of the meter-out pressure P_MOAm Of the particular actuator 205a on the basis of the target thrust F_TgtAm and the meter-in pressure P_MIAm of the particular actuator 205a, calculate the regeneration control valve target opening area A_TgtMoAm that is a target value of the opening area of the regeneration control valve 34 on the basis of the target meter-out pressure P_MorgtAm and the meter-out pressure P_MOAm of the particular actuator 205a, control the regulator 2a according to the pump target flow rate Q_Tgtpmp, control the plurality of directional control valves 10 and 11 according to the target meter-in opening areas A_TgtMIBm and A_TgtMIAm, and control the regeneration control valve 34 according to the regeneration control valve target opening area A_TgtMOAm.

According to the thus configured present embodiment, at the time of combined operation to simultaneously drive the arm cylinder 205a (the particular actuator that regenerates the flow of the return fluid) and the boom cylinder 204a (another actuator), the meter-in opening of each of the directional control valves 10 and 11 is adjusted according to the differential pressure across the directional control valve, thereby making it possible to supply the hydraulic fluid at a targeted flow rate to each actuator 204a or 205a. In addition, the meter-out opening of the arm directional control valve 11 is adjusted to input a targeted thrust to the arm cylinder 205a, thereby making it possible to prevent an excessive movement of an undriven member (the arm 205) due to inertia. Then, since the respective directional control valves 10 and 11 have a simple configuration formed by using identical valve bodies and identical housings in terms of the meter-in opening areas and the meter-out opening areas, costs can be reduced. This makes it possible to perform, with a simple configuration, speed control of the respective actuators 204a and 205a and thrust control of the particular actuator 205a that regenerates the flow of the return fluid, at the time of combined operation to simultaneously drive the particular actuator 205a and the other actuator 204a.

In addition, the work machine 901 in the present embodiment includes the bleed-off valve 36 that discharges the hydraulic working fluid delivered from the hydraulic pump 3, to the hydraulic working fluid tank 5, and the controller 94 is configured to calculate the bleed-off valve target opening area A_TgtBo that is a target value of the opening area of the bleed-off valve 36 on the basis of the input amounts of the operation devices 95a and 95b, calculate the estimated bleed-off flow rate Q_EstBo that is an estimated value of the passing flow rate of the bleed-off valve 36 on the basis of the bleed-off valve target opening area A_TgtBo and the pump pressure P_Pmp2/and calculate the pump target flow rate Q_Tgtpmp on the basis of the actuator target flow rates Q_TgtBm and Q_TgtAm, the estimated regeneration flow rate Q_EstRegAm, and the estimated bleed-off flow rate Q_EstBo. This makes it possible to prevent sudden movements of the actuators 204a and 205a at the start of operation of the actuators 204a and 205a since an excess amount of the delivered fluid of the hydraulic pump 3 is discharged to the hydraulic working fluid tank 5.

While an embodiment of the present invention has been mentioned in detail thus far, the present invention is not limited to the embodiment described above and incorporates various modification examples. For example, the embodiment described above is explained in detail in order to explain the present invention in an easy-to-understand manner, and the present invention is not necessarily limited to ones including all the constituent elements explained.

DESCRIPTION OF REFERENCE CHARACTERS

• • 1: First hydraulic pump
  • 1 a: Flow rate control command pressure port (regulator)
  • 2: Second hydraulic pump
  • 2 a: Flow rate control command pressure port (regulator)
  • 3: Third hydraulic pump
  • 3 a: Flow rate control command pressure port (regulator)
  • 5: Hydraulic working fluid tank
  • 6: Travel-right directional control valve
  • 7: Bucket directional control valve
  • 8: Second arm directional control valve
  • 9: First boom directional control valve
  • 10: Second boom directional control valve
  • 10 a, 10b: Pilot port
  • 11: First arm directional control valve
  • 11 a, 11b: Pilot port
  • 12: First attachment directional control valve
  • 13: Travel-left directional control valve
  • 14: Swing directional control valve
  • 15: Third boom directional control valve
  • 16: Second attachment directional control valve
  • 17: Confluence valve
  • 18 to 20: Main relief valve
  • 21 to 32: Check valve
  • 33: Arm regeneration valve
  • 34: Arm regeneration control valve
  • 34 a: Command pressure port
  • 35 to 37: Bleed-off valve
  • 36 a: Command pressure port
  • 40: Pump line
  • 41 to 48: Meter-in flow path
  • 50: Pump line
  • 51 to 58: Meter-in flow path
  • 60: Pump line
  • 61 to 66: Meter-in flow path
  • 71 to 74: Flow path
  • 75: Meter-out flow path
  • 76: Arm regeneration flow path
  • 80, 81: Flow path
  • 85: First pressure sensor
  • 86, 87: Second pressure sensor
  • 88, 89: Second pressure sensor
  • 91: Pilot pump
  • 92: Pilot relief valve
  • 93: Solenoid valve unit
  • 93 a to 93g: Solenoid valve
  • 94: Controller
  • 94 a: Boom target flow rate computing section
  • 94 b: Arm target flow rate computing section
  • 94 c: Arm estimated regeneration flow rate computing section
  • 94 d: Arm corrected target flow rate computing section
  • 94 e: Bleed-off valve target opening computing section
  • 94 f: Estimated bleed-off flow rate computing section
  • 94 g: Pump target flow rate computing section
  • 94 h: Pump control command output section
  • 94 i: Pressure state assessing section
  • 94 j: Boom directional control valve target meter-in opening computing section
  • 94 k: Boom directional control valve control command output section
  • 94 l: Arm directional control valve target meter-in opening computing section
  • 94 m: Arm directional control valve control command output section
  • 94 n: Required torque computing section
  • 940: Gravity torque computing section
  • 94 p: Inertia torque computing section
  • 94 q: Target torque computing section
  • 94 r: Target thrust computing section
  • 94 s: Arm target meter-out pressure computing section
  • 94 t: Arm regeneration control valve target opening computing section
  • 94 u: Arm regeneration control valve control command output section
  • 94 v: Bleed-off valve control command output section
  • 95 a: Boom operation lever (operation device)
  • 95 b: Arm operation lever (operation device)
  • 201: Track structure
  • 202: Swing structure (machine body)
  • 203: Work implement
  • 204: Boom
  • 204 a: Boom cylinder (actuator)
  • 205: Arm
  • 205 a: Arm cylinder (actuator)
  • 206: Bucket
  • 206 a: Bucket cylinder (actuator)
  • 207: Operation room
  • 208: Machine room
  • 209: Counter weight
  • 210: Control valve
  • 211: Swing motor
  • 212 to 216: Inertial measurement unit (posture sensor)
  • 901: Hydraulic excavator (work machine)
  • 902: Hydraulic drive system

Claims

1. A work machine comprising: a machine body;a work implement attached to the machine body;a hydraulic working fluid tank;a variable displacement hydraulic pump that sucks and delivers a hydraulic working fluid from the hydraulic working fluid tank;a regulator that controls a displacement of the hydraulic pump;a plurality of actuators that drive the work implement;a plurality of directional control valves that control a flow of a hydraulic fluid supplied from the hydraulic pump to the plurality of actuators;an operation device that gives an instruction for an action of the plurality of actuators;a regeneration flow path that connects a meter-out flow path connecting a particular directional control valve in the plurality of directional control valves to the hydraulic working fluid tank, and a meter-in flow path connecting the particular directional control valve to the hydraulic pump;a regeneration valve that is provided on the regeneration flow path and causes a return fluid of a particular actuator that is one of the plurality of actuators and corresponds to the particular directional control valve to merge with the meter-in flow path from the meter-out flow path;a regeneration control valve that is provided downstream of a point of branch from the regeneration flow path on the meter-out flow path and controls a passing flow rate of the regeneration valve by adjusting a flow rate of the hydraulic fluid returned from the particular actuator to the hydraulic working fluid tank; anda controller that controls the regulator, the plurality of directional control valves, and the regeneration control valve according to an input amount of the operation device, whereinthe work machine includes a first pressure sensor that senses a pump pressure that is a delivery pressure of the hydraulic pump,second pressure sensors that sense meter-in pressures and meter-out pressures of the plurality of actuators, anda posture sensor that senses postures and action states of the machine body and the work implement,the plurality of directional control valves are formed by using identical valve bodies and identical housings such that meter-in opening areas become smaller than meter-out opening areas in response to a valve displacement, andthe controller is configured to calculate an actuator target flow rate that is a target value of a flow rate of the hydraulic fluid supplied from the hydraulic pump to the plurality of actuators on a basis of the input amount of the operation device,calculate an estimated regeneration flow rate that is an estimated value of the passing flow rate of the regeneration valve on a basis of an opening area of the regeneration valve and a meter-in pressure and a meter-out pressure of the particular actuator,calculate a pump target flow rate that is a target value of a delivery flow rate of the hydraulic pump on a basis of the actuator target flow rate and the estimated regeneration flow rate,calculate a target meter-in opening area that is a target value of meter-in opening areas of the plurality of directional control valves on a basis of the actuator target flow rate, the pump pressure, and the meter-in pressure,calculate a target thrust that is a target value of a thrust of the particular actuator on a basis of the input amount of the operation device and an output value of the posture sensor,calculate a target meter-out pressure that is a target value of the meter-out pressure of the particular actuator on a basis of the target thrust and the meter-in pressure of the particular actuator,calculate a regeneration control valve target opening area that is a target value of an opening area of the regeneration control valve on a basis of the target meter-out pressure and the meter-out pressure of the particular actuator,control the regulator according to the pump target flow rate,control the plurality of directional control valves according to the target meter-in opening area, andcontrol the regeneration control valve according to the regeneration control valve target opening area.

2. The work machine according to claim 1, comprising: a bleed-off valve that discharges the hydraulic working fluid delivered from the hydraulic pump, to the hydraulic working fluid tank, whereinthe controller is configured to calculate a bleed-off valve target opening area that is a target value of an opening area of the bleed-off valve on a basis of the input amount of the operation device,calculate an estimated bleed-off flow rate that is an estimated value of a passing flow rate of the bleed-off valve on a basis of the bleed-off valve target opening area and the pump pressure, andcalculate the pump target flow rate on a basis of the actuator target flow rate, the estimated regeneration flow rate, and the estimated bleed-off flow rate.