JP5877986B2 - Control device for work vehicle - Google Patents

Description

  The present invention relates to a control device for a work vehicle having a hydraulically driven work device on a vehicle body.

  A work vehicle generally uses a chassis such as a cab-over truck as a base vehicle, and a hydraulically driven work device and a power source for operating the work device are provided on a vehicle body. In such a work vehicle, as a method of operating the work device provided on the vehicle body, the power taken out from the power take-off mechanism (PTO) attached to the transmission by driving the traveling engine of the work vehicle. It is generally known that a hydraulic pump is driven by using a hydraulic pump and a working device is operated by hydraulic oil discharged from the hydraulic pump (see, for example, Patent Document 1).

  An example of the work vehicle as described above is a digging pillar car used for electrical, communication, civil engineering, and the like (see, for example, Patent Document 2). This drilling column car is provided with a boom that can freely move up and down, extend and retract, and turn on a vehicle body that can travel, and a drilling device called an earth auger device is attached to the tip of this boom, To build a utility pole or the like on the ground by moving the earth auger device above the excavation position by rotating the boom up and down, expanding or contracting or turning, and rotating the auger screw attached to the lower part of the earth auger device It is now possible to excavate building pillar holes.

  In such a digging column car, the boom up / down motion, telescopic motion, turning motion, the winch device hoisting / lowering operation, and the earth auger device rotating operation are provided in the operation seat on the vehicle body. This is done by the operator operating each of the control levers. Each operation lever is connected to a control valve arranged corresponding to each hydraulic actuator of a working device such as a boom, and when the operator operates the operation lever, the hydraulic oil discharged from the hydraulic pump is Supply / discharge control is performed with the valve opening of the control valve in accordance with the operation amount, whereby each hydraulic actuator is operated.

  Separately from this, an accelerator pedal that the operator steps on is provided in the operation seat, and the engine speed as the power source of the hydraulic pump is controlled according to the amount of operation of the accelerator pedal, so that the engine speed is obtained. A configuration is also known in which hydraulic oil having a corresponding discharge flow rate is supplied from a hydraulic pump to a hydraulic actuator (see, for example, Patent Document 3). Recently, an electric motor as a power source is additionally mounted, and a work vehicle (so-called hybrid drive type work) in which a hydraulic pump different from the hydraulic pump driven by power extracted from the PTO is driven by the electric motor. Car) has also been developed.

JP 2003-12297 A JP 2009-227390 A Japanese Patent No. 3330908

  For example, when performing construction using the above digging pillar car, the pillar work may be performed at night when the traffic is relatively low in consideration of traffic congestion associated with the construction. In such night work, In particular, consideration for noise is required. In order to cope with such a work environment, the applicant has conventionally reduced the noise of a hybrid drive type work vehicle by driving only the electric motor while the engine is stopped in a work state where the required amount of hydraulic oil is small. However, when hydraulic oil is insufficient only by driving the electric motor, a control device has been developed that supplies the hydraulic actuator with sufficient hydraulic oil by driving the engine additionally. In this control device, the engine is added and started while the electric motor is rotationally driven at a rotational speed (for example, the maximum rotational speed) according to the amount of operation of the accelerator pedal. There is a problem that the operating speed of the hydraulic actuator increases at a stretch by the amount corresponding to the hydraulic oil discharged from the hydraulic pump, and the operability is lowered.

  The present invention has been made in view of such problems, and provides a work vehicle control device that improves operability by suppressing changes in the operating speed of the hydraulic actuator when the engine is started. Objective.

In order to solve the above-described problems, a control device for a work vehicle according to the present invention (for example, a digging column car 1 in the embodiment) is a hydraulic actuator (for example, the swing motor 23, the hoisting cylinder 24, the telescopic cylinder in the embodiment). 31, a winch motor 43, an auger motor 54) working devices (for example, the swivel base 20, the boom 30, the winch device 40, and the earth auger device 50 in the embodiment), and an electric motor that rotates by receiving electric power. An engine , a first hydraulic pump driven by receiving a rotational driving force from the electric motor, and supplying hydraulic oil to the hydraulic actuator, and a hydraulic pump driven by receiving the rotational driving force from the engine; A second hydraulic pump for supplying hydraulic oil to the tank and an operation for operating the working device. Hydraulic fluid from the first and second hydraulic pumps to the hydraulic actuator by changing the valve opening according to the operation performed on one operating means (for example, the operating lever 64 in the embodiment) and the first operating means. A control valve for performing supply / discharge control of the first operation amount, first operation amount detection means for detecting the operation amount of the first operation means (for example, lever operation position detector 101 in the embodiment), rotation of the electric motor and the engine Second operation means (for example, an accelerator pedal 66 in the embodiment) in which an operation for setting a speed is performed, and second operation amount detection means (for example, a pedal in the embodiment) for detecting an operation amount of the second operation means. and depressing the position detector 67), based on a detection result of said first and second operation amount detecting means, braking the driving of said electric motor and said engine Power source control means (for example, the controller 80 in the embodiment), and the power source control means has a first predetermined operation amount (for example, the fifth operation position in the embodiment) as the operation amount of the first operation means. L5), the electric motor is rotated at a first predetermined rotational speed (for example, the minimum rotational speed m1 in the embodiment) regardless of the operation amount of the second operation means, and the operation amount of the first operation means It controls the rotation of the electric motor in response to but an operation amount of the first predetermined operation amount or more der Ri and the operation amount of the second operating means second predetermined operation amount less sometimes the second operating means , the predetermined operation amount of the operation amount is the second operating means of the second state is the first predetermined operation amount or more first operating means (e.g., the fifth operating position A5 in the embodiment) over the When operated Is characterized in that the engine is additionally driven and the rotational speed of the electric motor is lowered so as to be lower than the rotational speed corresponding to the operation amount of the second operating means.

Incidentally, the power source control means includes a hydraulic oil amount per unit time discharged from the first hydraulic pump in accordance with the amount of operation of the second operating means before the said engine is driven, the engine is driven The rotational speed of the electric motor is controlled by the amount of operation of the second operating means so that the amount of hydraulic oil per unit time discharged from the first hydraulic pump and the second hydraulic pump becomes substantially the same. It is preferable that the rotation speed is lowered so as to be lower than the rotation speed according to the above.

Further, in the above-described invention, the power source control means causes the engine to move to the second engine regardless of the operation amount of the second operation means when the second operation means is operated while the engine is driven. It is preferable to rotate at a predetermined rotation speed (for example, the low-speed rotation speed e1 in the embodiment) and to control the rotation speed of the electric motor according to the operation amount of the second operation means.

Control apparatus for working vehicle according to the present invention, when the operation amount of the first operating means and the second operating means is operated beyond the second predetermined operation amount while the first predetermined operation amount or more, the engine And the rotational speed of the electric motor is reduced so as to be lower than the rotational speed corresponding to the operation amount of the second operating means. With this configuration, by activating the engine, when to supply the working oil to the hydraulic actuator from the second hydraulic pump in addition to the hydraulic oil from the first hydraulic pump, a first hydraulic pump in response to the activation of the engine The supplied hydraulic fluid can be reduced. Therefore, it is possible to improve the operability of the work vehicle by suppressing a change in the operating speed of the hydraulic actuator by suppressing a change in the amount of hydraulic oil supplied to the hydraulic actuator before and after starting the engine .

The power source control means controls the rotation speed of the electric motor so that the amount of hydraulic oil discharged from the first and second hydraulic pumps is substantially the same before and after the engine is started. It is preferable that the rotation speed is lowered so as to be lower than the rotation speed according to the amount. When configured in this manner, the operating speed of the hydraulic actuator hardly changes before and after the engine is started, so that the operability of the work vehicle can be further improved.

The power source control means rotates the engine at a second predetermined rotation speed when the second operation means is operated while the engine is driven, and the electric motor according to the operation amount of the second operation means. It is preferable to control the rotation. In the case of this configuration, the operating speed of the hydraulic actuator can be ensured by supplying the required amount of hydraulic oil from the first and second hydraulic pumps to the hydraulic actuator while suppressing noise generated from the engine. .

Further, when the required amount of work aggressive media is relatively small by supplying hydraulic fluid by driving the electric motor, on the other hand, only when the required amount of hydraulic oil can not cope with to the electric motor only drive increased engine Ru can der controlled to drive the. Therefore, a sufficient amount of hydraulic oil can be supplied to the hydraulic actuator while suppressing noise associated with the work, and the operating speed of the hydraulic actuator can be ensured.

It is a block diagram which shows the structure of the control apparatus which concerns on this invention. It is a side view which shows the digging pillar car as an example provided with the said control apparatus. It is a top view of the said digging pillar car. It is a rear view of the said digging pillar car. It is a schematic diagram for demonstrating the tilting operation position of an operation lever. It is a schematic diagram for demonstrating the depression operation position of an accelerator pedal. (A) is a graph showing the relationship between the lever operation amount and the electric motor rotation number, (b) is the relationship between the pedal depression amount and the electric motor rotation number, and (c) is the pedal depression amount and the engine rotation number. It is the graph which showed this relationship. It is the block diagram which showed the mode set to the said control apparatus. It is a graph which shows the example of control of an electric motor and an engine at the time of selecting quiet mode. It is a graph which shows another example of control of an electric motor at the time of selecting quiet mode. It is a graph which shows another example of control of an electric motor at the time of selecting quiet mode.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. FIGS. 2 to 4 show a hybrid drive type excavation pillar car 1 as an example of a work vehicle provided with a control device according to the present invention. First, an excavation pillar car using these drawings is shown. An overview of the overall configuration of 1 will be described. In addition, the rotation speed in this embodiment means the rotation speed per unit time.

  The excavation column car 1 includes tire wheels 11, 11,..., A truck-type vehicle body 10 that can be driven and operated from the driving cab 12, a swivel base 20 provided on the vehicle body 10, and the turning A telescopic boom (hereinafter simply referred to as “boom”) 30 whose base end is pivotally attached to the base 20 so as to be swingable up and down, and a wire rope 42 that is attached to the base end side of the boom 30 and wound up. A winch device 40 that performs the lowering and an earth auger device 50 that is attached to the side of the boom 30 and that excavates the pillar hole are configured.

  The swivel base 20 is attached to the rear part of the vehicle body 10 so as to be able to rotate 360 degrees around the vertical axis. The swivel motor 23 built in the vehicle body 10 is hydraulically driven to perform a horizontal turn operation via a gear (not shown). Can do. The boom 30 has a configuration in which a proximal boom 30a, an intermediate boom 30b, and a distal boom 30c are assembled in a nested manner, and each boom 30a, 30b and 30c can be moved relatively, and the whole boom 30 can be expanded and contracted in the axial direction.

  Further, a hoisting cylinder 24 is straddled between the base end boom 30a and the swivel base 20, and the hoisting cylinder 24 as a whole can be hoisted within the upper and lower surfaces by hydraulically driving the hoisting cylinder 24. On the vehicle body 10, behind the driving cab 12, a boom rest 39 that protrudes upward is disposed so as to abut against the lower surface of the boom 30 that has fallen in a fully contracted state and store and hold the boom 30. Here, the boom 30 has a three-stage expansion / contraction configuration, but may have a two-stage or four-stage or more multi-stage expansion / contraction configuration.

  The winch device 40 is attached to the upper surface of the base end portion of the base end boom 30a, and the wire rope 42 fed out from the winch drum 41 is hung on a rotatable sheave (not shown) and below the front end boom 30c. And a hook (not shown) is attached to the tip. A winch motor 43 is provided at a side portion of the winch device 40. The winch motor 43 is hydraulically driven to wind and unwind the wire rope 42, thereby lifting and lowering the hook at the tip of the wire rope 42. Can be lowered. A wire guard 44 for protecting the wire rope 42 is disposed along the axial direction of the boom 30 at the upper end portion of the boom 30.

  The earth auger device 50 is attached to the boom 30 via an auger support frame 51 that can be selectively connected to the proximal boom 30a and the distal boom 30c. This earth auger device 50 includes an auger support arm 52 pivotally connected to an auger support frame 51, a base frame 53 attached to the auger support arm 52, and an auger motor 54 with a speed reducer attached to the tip of the base frame 53. And an auger screw 55 that is rotationally driven by hydraulically driving the auger motor 54. Further, an auger support device 56 that fixes and holds the earth auger device 50 in a retracted state is disposed on the side surface of the proximal boom 30a. The earth auger device 50 can swing up and down in a vertical plane around the auger support arm 52. More specifically, the earth auger device 50 is stored along the side of the proximal boom 30a by the auger storage device 56. The ground auger device 50 can be removed from the auger storage device 56, and the auger screw 55 can be swung between the storage position and the vertical position with respect to the ground.

  When the earth auger device 50 is used (that is, when excavating a pillar hole), the earth auger device 50 is swung to a lower working position, and the auger support frame 51 is connected and tied to the tip boom 30a. Let As a result, the earth auger device 50 can move to a desired position together with the tip boom 30c. Then, by driving the auger motor 54 and rotating the auger screw 55, the auger screw 55 (boom tip) is linearly moved downward by interlocking the falling movement and the reduction movement of the boom 30, so Excavation work is performed.

  On the other hand, when the earth auger device 50 is not used, the earth auger device 50 is swung to the storage position along the side of the proximal boom 30a with the boom 30 fully retracted and stored and held by the auger support device 56. At the same time, the auger support frame 51 is connected to the proximal boom 30a. In this state where the earth auger device 50 is retracted, the wire rope 42 can be wound and unwound by the winch device 40. In the following description, the swivel base 20, the boom 30, the winch device 40, and the earth auger device 50 are collectively referred to as “working device”.

  Further, a hydraulic pressure supply unit 90 that supplies hydraulic oil to the vehicle body 10 to the turning motor 23, the hoisting cylinder 24, the telescopic cylinder 31, the winch motor 43, and the auger motor 54 (hereinafter collectively referred to as “hydraulic actuator”). And a controller 80 for controlling the operation of the work device.

  Outrigger jacks 13 are provided at four positions on the front, rear, left and right of the vehicle body 10, and the vehicle body 10 can be supported in a lifted state during work by projecting the outrigger jacks 13 downward and grounding. In addition, each outrigger jack 13 can be projected to the side (vehicle width direction) of the vehicle body 10, thereby making the vehicle body 10 more stable. The operation of the outrigger jack 13 is performed by operating an outrigger operation device 14 provided at the rear of the vehicle body 10.

  An operation seat 60 for operating the work devices (the turntable 20, the boom 30, the winch device 40, and the earth auger device 50) is provided on the side of the turntable 20 in the vehicle body 10. The operation seat 60 is attached to a side portion of the swivel base 20 and pivoted together with the swivel base 20. The operation seat 60 is disposed on the upper side of the base board 61 so that the operator faces the distal end side of the boom 30. A sitting chair 62 and an operation device 63 positioned in front of the chair 62 are provided. An operator can access the operation device 63 while sitting on the chair 62.

  The operating device 63 includes a turning operation lever 64a for turning the swivel base 20, a raising / lowering operating lever 64b for raising and lowering the boom 30, an extendable operation lever 64c for extending and retracting the boom 30, and a winch. A winch operating lever 64d for performing the hoisting / lowering operation of the device 40 and an auger operating lever 64e for rotating the earth auger device 50 are provided, and these five operating levers 64 are provided in the operation seat 60. Are arranged side by side with a predetermined interval in the width direction.

  Adjacent to the turning operation lever 64a, an attachment operation lever 65 is provided for performing an operation of pulling out a utility pole by a drawing machine (not shown) and an operation of an attachment to be attached as an option (hereinafter referred to as an operation lever 65). Then, the description of the operation lever 65 is omitted, and the illustration of the operation lever 65 is also omitted, but the operation lever 65 can also be applied as the first operation means defined in the claims).

  Each operation lever 64 can be tilted from the neutral position slightly tilted rearward when viewed from the operator toward the front (boom tip side) and the rear (worker side). For example, by turning the turning operation lever 64a forward, the turning motor 23 is driven to rotate in one direction to turn the turntable 20 in the counterclockwise direction, and by turning backward, the turning motor 23 is moved in the other direction. To rotate the swivel base 20 in the clockwise direction. Further, the hoisting operation lever 64b is tilted forward when viewed from the operator, the hoisting cylinder 24 is contracted to perform the tilting operation of the boom 30, and the hoisting cylinder 24 is extended by the tilting operation backward. The boom 30 is lifted up.

  Further, the telescopic operation lever 64c is tilted forward to cause the telescopic cylinder 31 to extend to operate the boom 30, and the rearward tilt is operated to contract the telescopic cylinder 31 to reduce the boom 30. Let the action take place. Further, the winch operation lever 64d is tilted forward to rotate the winch motor 43 in one direction to cause the wire rope 42 to be wound down, and tilted backward to rotate the winch motor 43 in the other direction. The wire rope 42 is wound up by driving. Further, the auger operation lever 64e is tilted forward to rotate the auger motor 54 in one direction to rotate the auger screw 55 in the reverse direction, and the auger operation lever 64e is tilted backward to move the auger motor 54 in the other direction. The auger screw 55 is rotated in the forward direction.

  As shown in FIG. 1, the swing motor 23 is connected to the winch motor 43 via the first control valve V1, the hoisting cylinder 24 via the second control valve V2, and the telescopic cylinder 31 via the third control valve V3. Is selectively discharged by the first hydraulic pump P1 or the second hydraulic pump P2 of the hydraulic pressure supply unit 90 (see FIG. 2) to the auger motor 54 via the fourth control valve V4 and via the fifth control valve V5. Oil (pressure oil) is supplied. In addition, since the driving force of the electric motor 71 mounted on the work vehicle is generally smaller than the driving force of the engine E, a second hydraulic pump P1 driven by the electric motor 71 is driven by the engine E. A hydraulic pump having a discharge capacity smaller than that of the hydraulic pump P2 (for example, one having a discharge capacity of about half) is used.

  Each of the control valves V1 to V5 is a manual valve that is mechanically coupled to each operation lever 64, so that the operator can directly adjust the valve opening. Each control valve V1 to V5 changes the valve opening degree by driving the spool with a drive direction and a drive amount corresponding to the operation direction and the tilting operation amount from the neutral position of each operation lever 64. The drive direction of each spool of the control valves V1 to V5 is related to the drive direction (extension / contraction direction or rotation direction) of the corresponding hydraulic actuator, and the drive amount (valve opening) of each spool is an operation supplied to the corresponding hydraulic actuator. It relates to the flow rate of oil (flow rate per unit time), that is, the operating speed of the hydraulic actuator.

  An accelerator pedal 66 is provided on the floor surface of the base board 61 in the operation seat 60 so that an operator sitting on a chair 62 can step on with his / her foot. The depression position of the accelerator pedal 66 is detected by a pedal depression position detector 67 and output to the controller 80 as an accelerator signal. In response to the accelerator signal from the pedal depression position detector 67, the controller 80 is electrically operated in accordance with the depression operation amount from the neutral position where the accelerator pedal 66 is not depressed (the pedal is not placed on the accelerator pedal 66). The operation of the motor 71 and the engine E is controlled (details will be described later).

  In this digging pillar working vehicle 1, a battery unit 70 provided on the vehicle body 10 is used as a power source for the first hydraulic pump P1, and a power source for the second hydraulic pump P2 is provided at the lower portion of the vehicle body 10. A traveling engine E can be used, and an engine E, a battery unit 70, a controller 80, a hydraulic pressure supply unit 90, and the like are provided as an operating mechanism of a work device (hydraulic actuator) such as a boom 30.

  As shown in FIG. 1, the power of the engine E is shifted by a transmission TM and transmitted to the tire wheel 11 via a propeller shaft (not shown). The transmission TM includes a power take-off mechanism PTO. When an operation (on operation) is performed to displace the PTO operation lever 15 in the driving cab 12 from the off position to the on position, the power take-off mechanism PTO By actuating the mechanism portion, the drive destination of the engine E can be switched from the tire wheel 11 to the second hydraulic pump P2. A PTO switch 16 is provided in the vicinity of the PTO operation lever 15. When the PTO operation lever 15 is turned on, the PTO switch 16 is turned on to detect the state of taking out the power of the engine E. The

  The engine E is connected to an electronic control unit ECU that controls each part of the engine. The electronic control unit ECU controls the rotational speed of the engine E (that is, the rotational speed of the second hydraulic pump P2 connected thereto) by performing throttle opening control, fuel injection control, and the like of the engine E. 2 Controls the discharge flow rate (and discharge pressure) of the hydraulic oil discharged from the hydraulic pump P2.

  The battery unit 70 receives an electric motor 71 connected to the first hydraulic pump P1, a body part battery 72 that stores electric power for driving the electric motor 71, and power supplied from the body part battery 72. And a motor control device 73 for controlling the operation of the electric motor 71.

  The body part battery 72 is composed of a plurality of power supply batteries, and each power supply battery is connected in series with each other, for example, with a predetermined voltage of 48 [V] and sufficient electric power to perform the work for one day. This is a DC power supply capable of charging and holding the capacity 280 [Ahr]. This body part battery 72 is connected to a charger (not shown) provided at the lower part of the vehicle body 10, and the power plug of this charger is connected to a power outlet of a sales office or the like, thereby The three-phase AC power supplied from the plug is converted into a direct current of a predetermined voltage and supplied to the body part battery 72 to charge each power source battery of the body part battery 72.

  The motor control device 73 is composed of, for example, a control circuit using an inverter control system. By converting the DC power supplied from the body part battery 72 into AC power (inverter output) having a voltage value corresponding to the command signal from the controller 80 and supplying the AC power to the electric motor 71, the rotational speed of the electric motor 71 ( That is, the rotational speed of the first hydraulic pump P1 connected thereto is controlled to the rotational speed corresponding to the inverter output, and as a result, the discharge flow rate (and discharge pressure) of the hydraulic oil discharged from the first hydraulic pump P1. To control.

  The controller 80 is turned on and off via a power supply circuit 81 provided on the vehicle body 10. The power supply circuit 81 includes the above-described PTO switch 16 that closes (turns on) the switch contact based on the operation of the PTO operation lever 15, and the PTO switch is operated when the PTO operation lever 15 is turned on. When the switch contact of 16 is closed, the controller 80 is connected to the chassis battery 17 for running control that supplies power to the vehicle-side electrical device such as the engine E, and the controller 80 is turned on. It is configured to be.

  The chassis battery 17 is connected to a generator G (for example, an alternator) that generates electricity by rotating the engine E, and is charged by supplying the generated power. Further, a potential signal based on the driving state of the engine E is output from the generator G to the controller 80, and the controller 80 can determine whether the engine E is driven or stopped based on the potential signal from the generator G. ing.

  In addition, the motor control device 73 is electrically connected to the chassis battery 17 via a power switch 68 provided on the operation seat 60 and capable of being turned on / off. Electric power is supplied from the battery 17 to the motor control device 73, and the motor control device 73 is turned on.

  The hydraulic pressure supply unit 90 is taken out by an oil tank T that stores a predetermined amount of hydraulic oil, a mechanical first hydraulic pump P1 that is driven by the power of the electric motor 71 in the battery unit 70, and a power take-off mechanism PTO. The mechanical second hydraulic pump P2 driven by the power of the engine E and the control valves (manual valves) V1 to V5 mechanically connected to the operation levers 64 are configured. Thus, the hydraulic pressure supply unit 90 includes two hydraulic pumps P1 and P2 for operating the working device (hydraulic actuator).

  As shown in FIG. 8, the controller 80 is preset with a plurality of modes related to drive control of the electric motor 71 and the engine E. These modes can be selected by operating a power source selection switch 69 provided in the operation device 63. The electric mode DM is a mode in which hydraulic oil is discharged only from the first hydraulic pump P1 by driving the electric motor 71 while the engine E is stopped. Therefore, when the electric mode DM is selected, the noise accompanying the work can be reduced by stopping the engine that has a relatively large noise during driving. The engine mode EM is a mode in which hydraulic oil is discharged only from the second hydraulic pump P2 by driving the engine E with the electric motor 71 stopped. Therefore, when the engine mode EM is selected, a large amount of hydraulic oil can be discharged from the second hydraulic pump P2 to operate the work device at a sufficient operating speed.

  The hybrid mode HM is a mode in which hydraulic oil is discharged from both the first hydraulic pump P1 and the second hydraulic pump P2 by driving the electric motor 71 and the engine E in combination. The hybrid mode HM is classified into a quiet mode SM that drives the engine E at a relatively low constant rotational speed, and a power mode PM that drives the engine E at a higher rotational speed than the quiet mode. Further, the power mode PM includes the engine rotation constant mode CM for driving the engine E at a constant rotation speed higher than that of the quiet mode SM, and the rotation speeds of the electric motor 71 and the engine E according to the depression amount of the accelerator pedal 66. The engine rotation variable mode VM is variably controlled.

  When the quiet mode SM of the hybrid mode HM is selected, as will be described later, basically, the electric motor 71 is driven to discharge the hydraulic oil from the first hydraulic pump P1, and a large amount of hydraulic oil. Only when the engine is required, the engine E is additionally started and controlled to rotate at a relatively low constant rotational speed. Thus, in the quiet mode SM, when the required amount of hydraulic oil is relatively small, only the electric motor 71 is driven to reduce noise, and the engine E is added only when a large amount of hydraulic oil is required. Thus, the control is performed to ensure the supply amount of hydraulic oil while suppressing the generation of noise.

  The constant engine speed mode CM is common to the quiet mode in that the engine E is driven only when a large amount of hydraulic oil is required, but the engine E is driven at a constant rotational speed higher than the quiet mode SM. It is different from the quiet mode SM. Therefore, when the constant engine rotation mode CM is selected, the engine E can be driven to supply a large amount of hydraulic oil to the hydraulic actuator, thereby improving the working efficiency.

  In the engine rotation variable mode VM, the engine E is always driven, and the rotational speeds of the electric motor 71 and the engine E are controlled in accordance with the depression amount of the accelerator pedal 66. Therefore, when the engine rotation variable mode VM is selected, hydraulic oil corresponding to the depression operation amount of the accelerator pedal 66 is supplied from both of the first hydraulic pump P1 and the second hydraulic pump P2, thereby The operating speed can be secured.

  As described above, the electric mode DM, the engine mode EM, and the hybrid mode HM are selected (when the hybrid mode HM is selected, the quiet mode SM, the engine rotation constant mode CM, and the engine rotation variable mode VM are selected). This is performed by operating a power source selection switch 69 provided in the device 63. The hydraulic oil corresponding to the selected mode sucks the hydraulic oil from the oil tank T and discharges it to the hydraulic actuators via the control valves V1 to V5. A relief valve (not shown) and a check valve (not shown) are interposed on the oil passages between the hydraulic pumps P1 and P2 and the control valves V1 to V5.

  As the power source selection switch 69, for example, a toggle switch that can be tilted or a dial switch that can be rotated can be used, and the switch can be switched to a tilting operation position or a rotation operation position corresponding to a desired mode. The desired mode can be selected by operating. In the power source selection switch 69, when both the PTO switch 16 and the power switch 68 are turned on, that is, when both the first hydraulic pump P1 and the second hydraulic pump P2 can be driven. The selection is valid only.

  In the digging column 1 configured as described above, the two power sources are controlled, and the hydraulic pumps P1 and P2 are controlled based on the tilting operation amount of each operation lever 64 and the depression operation amount of the accelerator pedal 66. A control device for variably adjusting the discharge flow rate is provided. The configuration of this control apparatus will be described below with additional reference to FIGS.

  The control device according to the present embodiment includes the hydraulic actuator, the operation lever 64, the accelerator pedal 66, the pedal depression position detector 67, the engine E, the battery unit 70, the controller 80, the hydraulic supply unit 90, and the power source selection switch 69 described above. In addition, a lever operation position detector 101 is provided. Among the members constituting the control device, the configurations of the pedal depression position detector 67 and the lever operation position detector 101 will be described in detail below.

  The lever operation position detector 101 includes, for example, a potentiometer, an encoder, a limit switch, or the like. As shown in FIG. 5, the operation lever 64 is positioned at the neutral position LN and the first operation position L1 to the fifth operation position L5. It is configured to be detectable. The neutral position LN is a position when the operation lever 64 is not operated (the operation lever 64 is not touched). When the operation lever 64 is in this position, the control valves V1 to V5 are fully closed. It is. The first operation position L1 is set to a position where the operation is slightly tilted from the neutral position LN, that is, a position where the operation can be detected by touching the operation lever 64. The second operation position L2 to the fifth operation position L5 are set to positions at which it is possible to detect stepwise that the operation lever 64 has been tilted more greatly than the first operation position L1. The fifth operation position L5 is set to a position where it can be detected that the operation lever 64 has been operated to the vicinity of the maximum tilt position (full lever position). The detection result in the lever operation position detector 101 is output to the controller 80 electrically connected to the lever operation position detector 101.

  Here, as the first operation position L1, for example, a play range between the neutral position LN and an operation start position at which the operation lever 64 is operated by a predetermined angle to start the operation of the mechanical control valves V1 to V5. Set within. As described above, each operation lever 64 can be tilted in the front-rear direction. Each operation lever 64 includes a lever operation position detector 101 for detecting a front operation and a lever operation position detection for detecting a rear operation. In FIG. 1, one lever operation position detector 101 is illustrated for each operation lever 64.

  The pedal depression position detector 67 is composed of, for example, a potentiometer, an encoder, a limit switch, or the like. As shown in FIG. 6, the accelerator pedal 66 is positioned at the neutral position AN and the first operation position A1 to the sixth operation position A6. It is configured to be detectable. The neutral position AN is a position when the accelerator pedal 66 is not depressed (the foot is not placed on the accelerator pedal 66). The first operation position A1 is set to a position where the stepping operation is slightly performed from the neutral position AN, that is, a position where it is possible to detect that the stepping operation is started by placing the foot on the accelerator pedal 66. The second operation position A2 to the fifth operation position A5 are set to positions at which it can be detected in steps that the accelerator pedal 66 has been depressed more than the first operation position A1. The fifth operation position A5 is set to a position where it can be detected that the accelerator pedal 66 has been depressed slightly before the maximum depression position. The sixth operation position A6 is set to a position where it can be detected that the accelerator pedal 66 has been depressed further than the fifth operation position A5 and has been depressed to the maximum depression position (solid depression position). The detection result in the pedal depression position detector 67 is output to a controller 80 electrically connected to the pedal depression position detector 67.

  The control device mounted on the digging pillar car 1 has a feature in the control when the quiet mode SM of the hybrid mode HM is selected, and this feature will be described below. Before describing an example of control when the quiet mode SM is selected, a one-to-one relationship between the operating means and the power source will be described with reference to FIG.

  FIG. 7A shows the relationship between the operation amount of the operation lever 64 and the rotation speed of the electric motor 71. As can be seen from FIG. 7A, when the operation lever 64 is tilted to the first operation position L1, the electric motor 71 is started at the minimum rotation speed m1 and operated above the first operation position L1. In this case, the electric motor 71 is driven to rotate at the minimum rotation number m1 regardless of the operation amount of the operation lever 64. FIG. 7 does not show the relationship between the operation amount of the operation lever 64 and the rotation speed of the engine E, because the operation amount of the operation lever 64 is not directly related to the control of the rotation speed of the engine E. is there.

  A straight line A indicated by a two-dot chain line in FIG. 7B indicates the depression amount of the accelerator pedal 66 and the rotation speed of the electric motor 71 when the operation amount of the operation lever 64 is lower than L5 (see FIG. 7A). Shows the relationship. As can be seen from the straight line A, when the operation amount of the operation lever 64 is less than L5, the rotation speed of the electric motor 71 is maintained at the minimum rotation speed m1 regardless of the depression amount of the accelerator pedal 66. A broken line B in FIG. 7B shows the relationship between the depression amount of the accelerator pedal 66 and the rotation speed of the electric motor 71 when the operation amount of the operation lever 64 exceeds L5 (see FIG. 7A). ing. As can be seen from this broken line B, in a state where the operation amount of the operation lever 64 exceeds L5, the rotation speed of the electric motor 71 is controlled in, for example, five stages according to the depression operation amount of the accelerator pedal 66. The control shown in FIG. 7B is the control when the electric mode DM is selected.

  FIG. 7C shows the relationship between the depression amount of the accelerator pedal 66 and the rotational speed of the engine E. The control shown in FIG. 7C is a control when the engine mode EM is selected. In this case, the engine E is stopped in accordance with the stepping operation amount of the accelerator pedal 66 while the electric motor 71 is stopped. The number of rotations is controlled over, for example, four stages. When the engine mode EM is selected, the operation amount of the operation lever 64 is not directly related to the rotation speed control of the engine E.

  The control when the power source selection switch 69 is operated and the quiet mode SM of the hybrid mode HM is selected will be described with reference to the control example shown in FIG. When the operation lever 64 and the accelerator pedal 66 are operated with this mode selected, the rotational speeds of the electric motor 71 and the engine E are controlled by combining the graphs of FIGS. The In FIG. 9, the operator sitting on the chair 62 tilts the operating lever 64 corresponding to the hydraulic actuator to be operated, and then depresses the accelerator pedal 66 to adjust the operating speed of the hydraulic actuator. The case of operating is illustrated.

  Before the control shown in FIG. 9 is performed, in order to perform a desired work (for example, a pole pole work), an operator who has driven this work vehicle and arrived at a target work site, In the operating state, the PTO operation lever 15 is first operated. As a result, the second hydraulic pump P2 can be driven to rotate by receiving the power of the engine E taken out by the power take-off mechanism PTO, and the PTO switch 16 is turned on so that the chassis battery 17 transfers to the controller 80. Power is supplied and the controller 80 is turned on.

  Further, when the operator turns on the power switch 68 of the operation seat 60, electric power is supplied from the chassis battery 17 to the motor control device 73 of the battery unit 70, and the power of the motor control device 73 is turned on. 1 The hydraulic pump P1 can be driven to rotate by an electric motor 71 driven by receiving power supply from the battery unit 70. Thus, after both the first hydraulic pump P1 and the second hydraulic pump P2 can be rotated, the power source selection switch 69 is operated to select the quiet mode SM.

  First, when it is detected that the operation lever 64 is slightly tilted from the neutral position LN to the first operation position L1 at time t1 shown in FIG. 9, this detection result is detected as a lever operation position detector. 101 to the controller 80. When this detection result is input, the controller 80 controls the electric motor 71 to a certain minimum rotational speed m1 via the motor control device 73, and the minimum flow rate Q1 necessary for the operation of the hydraulic actuator from the first hydraulic pump P1 is set. Discharge hydraulic fluid.

  From time t1 to time t2, the operation lever 64 is gradually tilted from the first operation position L1 and tilted until it is located in the vicinity of the fifth operation position L5 (maximum tilt position). Until reaching the fifth operation position L5, the electric motor 71 is controlled to rotate at the minimum rotation speed m1 set at the time t1 regardless of the tilting operation position of the operation lever 64. Although not shown in FIG. 9, if the accelerator pedal 66 is depressed at time t1 to t2, similarly, the minimum rotation speed is obtained when the operation lever 64 has not reached the fifth operation position L5. Control to rotate the electric motor 71 at m1 is performed. That is, until the operation lever 64 reaches the fifth operation position L5, control is performed to rotate the electric motor 71 at the minimum number of rotations m1 regardless of the tilting operation amount of the operation lever 64 and the accelerator pedal 66. Is called. By this control, it is possible to prevent the hydraulic oil exceeding the valve opening from being supplied to the control valves V1 to V5 and reduce the hydraulic oil relieved by the control valves V1 to V5, thereby reducing the energy loss. .

  When the operation lever 64 is tilted until it reaches the fifth operation position L5 at time t2, the detection result is output from the lever operation position detector 101 to the controller 80. For example, when the accelerator pedal 66 is depressed from the neutral position AN to the first operation position A1 at this time t2, the detection result is output from the pedal depression position detector 67 to the controller 80. The controller 80 uses the two detection results (the detection result that the operation lever 64 is tilted to the fifth operation position L5 and the detection result that the accelerator pedal 66 is depressed to the first operation position A1). In response, it is determined that the operator is requesting hydraulic fluid having a flow rate exceeding the minimum flow rate Q1. Based on this determination, the controller 80 controls the rotation of the electric motor 71 from the control for maintaining the minimum rotation speed m1 regardless of the tilting operation amount of the operating lever 64 and the depression operation amount of the accelerator pedal 66. The control is switched to a control in which the rotation speed is changed stepwise according to the stepping operation amount.

  In FIG. 9, at time t2, the detection result that the operation lever 64 is tilted to the fifth operation position L5 and the detection result that the accelerator pedal 66 is depressed to the first operation position A1 are simultaneously detected. Although the case where it detects is illustrated, when these two detection results are detected at different timings, the electric motor 71 corresponds to the depression operation amount of the accelerator pedal 66 when the two detection results are aligned. The control can be switched to a stepwise change in the rotation speed.

  From time t2 to t3, the accelerator pedal 66 is gradually depressed from the first operation position A1 and is depressed to the vicinity of the fifth operation position A5 while the operation lever 64 is tilted to the fifth operation position L5. Is done. While this depression operation is being performed, a detection result corresponding to the depression operation position of the accelerator pedal 66 is output from the pedal depression position detector 67 to the controller 80, and the controller 80 corresponds to the depression operation amount of the accelerator pedal 66 as described above. Thus, control is performed to change the rotational speed of the electric motor 71 stepwise. As a result, it is possible to control the operating speed of the hydraulic actuator in accordance with the depression operation amount of the accelerator pedal 66 while suppressing the noise generated from the digging column car 1. In addition, the rotation control of the electric motor 71 at this time is performed on the precondition that the operation lever 64 has reached the fifth operation position L5 (the valve opening is fully open). The hydraulic oil relieved at V5 is reduced, and energy loss is reduced.

  When it is detected at time t3 that the accelerator pedal 66 has been depressed to the fifth operation position A5, the controller 80 causes the electric motor 71 to rotate at the maximum rotation speed m2 corresponding to the fifth operation position A5. Is done. By doing so, the hydraulic oil discharged from the first hydraulic pump P1 is increased, and the hydraulic oil at the maximum flow rate Q2 (> minimum flow rate Q1) corresponding to the maximum rotation speed m2 is discharged.

  Even when the electric motor 71 is rotated at the maximum rotation speed m2 as described above at time t4, the operating speed of the hydraulic actuator is lower than the intended speed (the supply amount of hydraulic oil is insufficient). In this case, the accelerator pedal 66 is further stepped on while the operation lever 64 is tilted to the fifth operation position L5 by the operator, and the stepping operation reaches the sixth operation position A6 beyond the fifth operation position A5. Is done. Here, when the accelerator pedal 66 is stepped on from the fifth operation position A5 to the sixth operation position A6, a larger stepping force is required than when the accelerator pedal 66 is depressed between the neutral position AN and the fifth operation position A5. It is comprised as needed, and it is prevented from stepping on from the 5th operation position A5 to the 6th operation position A6.

  In this manner, when the accelerator pedal 66 is depressed to the sixth operation position A6 in a state where the operation lever 64 is tilted to the fifth operation position L5, the controller 80 controls the electric motor 71 to the maximum rotational speed m2. It is determined that hydraulic oil is required in excess of the flow rate when rotating at. The controller 80 performs control to start the engine E based on the tilting operation amount of the operation lever 64 and the depression operation amount of the accelerator pedal 66 at this time, for example, to rotate at the low speed e1 during idling. A command signal is output from the controller 80 to the motor control device 73 in response to the start of the engine E, so that the rotational speed of the electric motor 71 is lower than the maximum rotational speed m2 corresponding to the amount of depression of the accelerator pedal 66. AC power (inverter output) to be reduced to the rotational speed is supplied from the motor control device 73 to the electric motor 71. Here, for example, control is performed to reduce the rotational speed of the electric motor 71 so that the discharge amount from the first hydraulic pump P1 is reduced by the discharge amount from the second hydraulic pump P2 accompanying the start of the engine E, for example. . In this way, by performing control to reduce the rotation speed of the electric motor 71 in response to the start of the engine E, when the engine E is started, before the engine E is started (time t3 to time t4). ), Approximately the same amount of hydraulic oil as that supplied to the hydraulic actuator can be supplied to the hydraulic actuator. Therefore, before and after starting the engine E, it becomes possible to prevent the operating speed of the hydraulic actuator from changing and improve the operability, so that the operator does not feel uncomfortable.

  At time t4, when an inverter output for reducing the rotation speed of the electric motor 71 is output from the motor control device 73 to the electric motor 71, the time is actually shown as a line 91 indicated by a two-dot chain line in FIG. The rotational speed of the electric motor 71 decreases to the target rotational speed with a delay of, for example, about 50 msec (milliseconds) from t4. On the other hand, when control is performed by the controller 80 to start the engine E and rotate at the low speed e1 at time t4, in practice, for example, from the time t4, for example, several The engine E reaches the low speed e1 (target speed) with a delay of about msec. As described above, the electric motor 71 and the engine E reach the target rotational speed with a slight time lag after being controlled at the time t4, but the mutual time lag suppresses the change in the operating speed of the hydraulic actuator (hydraulic actuator Therefore, operability is ensured.

  At time t5, the accelerator pedal 66 is returned from the sixth operation position A6 to the vicinity of the neutral position AN. This operation is performed for associating the depression operation amount of the accelerator pedal 66 with the rotation speed of the electric motor 71. By this association, the electric operation corresponding to the depression operation amount of the accelerator pedal 66 is performed after time t5. The rotation of the motor 71 can be controlled.

  From time t5 to t6, the accelerator pedal 66 is depressed while the operation lever 64 is tilted to the fifth operation position L5 so that the hydraulic actuator has a desired operating speed. At this time, the controller 80 maintains the rotation speed of the engine E at the low-speed rotation speed e1 at the start-up regardless of the depression operation amount of the accelerator pedal 66, and the rotation speed corresponds to the depression operation amount of the accelerator pedal 66. The rotational speed of the electric motor 71 is controlled stepwise. By this control, the hydraulic oil corresponding to the low-speed rotation speed e1 is discharged from the second hydraulic pump P2 having a relatively large capacity, and the hydraulic oil corresponding to the depression operation amount of the accelerator pedal 66 is discharged from the first hydraulic pump P1. By discharging, it is possible to supply the hydraulic actuator with an amount of hydraulic oil necessary for operating the hydraulic actuator at a desired operating speed. Therefore, by rotating the engine E at the low speed e1, the noise associated with the driving of the engine E is reduced. For example, while the auger screw 55 is rotated, the falling motion and the reduction motion of the boom 30 are linked to each other. Even when excavation work is performed, the hydraulic oil does not run short, and the hydraulic actuator can be operated at a speed intended by the operator.

  At time t6, it is detected that the accelerator pedal 66 has been returned to the neutral position AN by releasing the foot from the accelerator pedal 66, and thereafter, at time t7, the operation lever 64 is neutralized by releasing the hand. It is detected that the position has been returned to the position LN. As described above, after a predetermined time (for example, several seconds) has elapsed from the time 7 when it is detected that both the accelerator pedal 66 and the operation lever 64 are returned to the neutral position, the control for stopping the engine E at time t8 is performed. Is called.

  In this way, by performing control to stop the engine E after a lapse of a predetermined time from the time t7, for example, the operation to the accelerator pedal 66 and the operation lever 64 is temporarily stopped assuming that the target work is completed. However, when the additional work is attempted after rethinking, the engine E remains in the driving state, so that the work can be resumed without starting the engine E again. Thereby, it is possible to prevent the engine E from being frequently started and stopped, to reduce the burden on the starter of the engine E, and to reduce noise generated at the time of starting and stopping.

  The operator puts his / her feet on the accelerator pedal 66 (the accelerator pedal 66 is positioned at the first operation position A1) or touches the operation lever 64 (the operation lever 64 is at the first operation position L1). It is possible to prevent the engine E from being automatically stopped. For this reason, after the engine E is once started, the operator puts his / her feet on the accelerator pedal 66 when he / she does not want to stop the engine E because he / she plans to resume the work immediately after the work is temporarily interrupted. Alternatively, by touching the operation lever 64, the engine E can be prevented from being automatically stopped, and the next operation can be performed smoothly.

  In FIG. 9, an example in which the rotation speed of the electric motor 71 is controlled stepwise so that the rotation speed corresponds to the depression operation amount of the accelerator pedal 66 at time t5 to t6 after the engine E is started. Although shown, in addition to this control example, for example, the control shown in FIG. 10 is also possible. The control example shown in FIG. 10 is different from FIG. 9 only in the control from time t4 to time t5, and the other control is the same as the control shown in FIG. In FIG. 10, at the time t4, the engine E is started and the rotation speed of the electric motor 71 is maximized based on the accelerator pedal 66 being depressed to the sixth operation position A6 as in FIG. Control to decrease from the rotational speed m2 is performed. After that, for example, when it is detected that the accelerator pedal 66 is depressed to the sixth operation position A6 in order to increase the operating speed of the hydraulic actuator to the maximum speed in the quiet mode, the controller 80 detects this. Based on the result, control is performed to increase the rotational speed of the electric motor 71 step by step (time t4 to time t5 in FIG. 10). Since the control for increasing the rotational speed of the electric motor 71 is performed in this way, after the engine E is started, the operator can increase the operating speed of the hydraulic actuator without once returning the accelerator pedal 66 to the neutral position AN. Can do.

  Further, as a control example different from FIG. 9, for example, the control shown in FIG. 11 is also possible. In FIG. 11, the engine E is started based on the fact that the accelerator pedal 66 is depressed to, for example, the third operation position A3 in a state where the operation lever 64 is operated to the fifth operation position L5 (time t3). At the same time, control is performed to reduce the rotational speed of the electric motor 71 from the intermediate rotational speed m3 corresponding to the depression operation amount of the accelerator pedal 66 at this time. Thereafter, when the accelerator pedal 66 is depressed in the range from the third operation position A3 to the sixth operation position A6 at time t3 to time t4, the rotation speed of the electric motor 71 is set according to the depression operation amount of the accelerator pedal 66. It is controlled stepwise in the range from the minimum rotation speed m1 to the maximum rotation speed m2.

  In the control shown in FIG. 11, the engine E is started based on the depression of the accelerator pedal 66 up to the middle position, and when the accelerator pedal 66 is further depressed, the engine speed is increased. The rotational speed of the electric motor 71 is controlled according to the stepping operation amount while maintaining the low rotational speed e1. Therefore, at time t2 to time t5, the amount of hydraulic oil corresponding to the depression operation amount of the accelerator pedal 66 is supplied from only the first hydraulic pump P1 (time t2 to time t3), or the first hydraulic pump P1 and the second hydraulic pressure. It can be supplied from the pump P2 (time t3 to time t5) to the hydraulic actuator, and the hydraulic actuator can be operated at the operating speed intended by the operator. The control shown in FIG. 11 uses a pedal depression position detector 67 that can detect the depression position of the accelerator pedal 66 more finely (for example, in 11 steps), so that the hydraulic actuator corresponds to the depression operation amount of the accelerator pedal 66. The amount of hydraulic oil supplied to the engine can be finely controlled.

  FIG. 11 exemplifies control for stopping the engine E at time t7 after a predetermined time has elapsed from time t6 when it was detected that both the accelerator pedal 66 and the operation lever 64 were returned to the neutral position. However, the following control is also possible. That is, at time t4, when it is detected that the accelerator pedal 66 is returned to the third operation position A3 while the engine E is being driven, the engine E is stopped and the rotation speed of the electric motor 71 is set. It is also possible to control to increase the intermediate rotational speed m3 corresponding to the third operation position A3. In the subsequent time t4 to time t5, control is performed in which the rotational speed of the electric motor 71 is changed stepwise in the range from the intermediate rotational speed m3 to the minimum rotational speed m1 in accordance with the amount of depression of the accelerator pedal 66. . According to this control, although the engine E is additionally driven, it is possible to improve the usability by associating the operation amount of the accelerator pedal 66 with the amount of hydraulic oil supplied to the hydraulic actuator.

  In the above-described embodiment, the control for reducing the rotational speed of the electric motor 71 to the vicinity of the minimum rotational speed m1 corresponding to the start of the engine E has been described as an example, but the present invention is not limited to this control. . When the engine E is started, the hydraulic oil discharged from the first hydraulic pump P1 may be reduced so as to suppress a change in the operating speed of the hydraulic actuator. For example, the minimum rotational speed m1 is less than the maximum rotational speed m2. It is possible to control to reduce to an arbitrary number of revolutions.

  In the above-described embodiment, the configuration in which the tilt operation position of the operation lever 64 is detected by the lever operation position detector 101 has been exemplified. However, a configuration using a detector that detects the tilt operation amount of the operation lever 64 can be used instead. good. Similarly, instead of the configuration where the pedal depression position detector 67 detects the depression operation position of the accelerator pedal 66, a configuration using a detector that detects the depression operation amount of the accelerator pedal 66 may be used. As the detector, an optical type (non-contact operation type) or a mechanical type (contact operation type) can be used.

  In the above-described embodiment, the configuration in which the rotation speed of the electric motor 71 is controlled stepwise according to the depression amount of the accelerator pedal 66 has been described as an example. However, instead of this control, the rotation speed is continuously changed. The structure to control may be sufficient.

  In the above-described embodiment, the control method in which the engine E is automatically stopped after a predetermined time after stopping the operation of the accelerator pedal 66 and the operation lever 64 has been described as an example. It is not limited to. For example, after stopping the operation to the accelerator pedal 66 and the operation lever 64, you may perform control which stops the engine E immediately. When this control is performed, useless fuel consumption in the engine E can be suppressed.

  Further, in the above-described embodiment, the case where the control valves V1 to V5 are configured by manual valves that are mechanically connected and interlocked with the operation lever 64 is described as an example, but the present invention is not limited to this. For example, the control valves V1 to V5 may be composed of solenoid valves (proportional electromagnetic directional flow control valves), and the controller may drive the spool of the control valve based on an operation signal output by operating the operation lever. Furthermore, in the above-described embodiment, the valve openings of the control valves V1 to V5 are exemplified as changing continuously (linearly), but the valve openings may be changed stepwise (at least in two steps).

  Moreover, although the example which mounted the operation lever 64 which can be tilted in the front-back direction was shown in the above-mentioned embodiment, this invention is not limited to this structure. For example, an operation lever that can be tilted in the left-right direction may be used. In addition, a joystick-type operation lever that can be tilted in a plurality of directions and twisted around an axis, or a plurality of preset levers. You may comprise the position lever which can be selectively operated to a position position, the volume switch which can be rotated.

  In the above-described embodiment, the example in which the accelerator pedal 66 that can be stepped on is adopted as the setting means for setting the rotation speed of the electric motor 71 has been described, but the present invention is not limited to this configuration. For example, it is possible to adopt a setting means of a type in which the operation knob is operated to slide or a type in which the operation knob is rotated.

  9 to 11, until the operation lever 64 reaches the fifth operation position L5 (full lever position) (time t1 to t2), regardless of the tilt operation amount of the operation lever 64 and the accelerator pedal 66, The configuration for performing the control of rotating the electric motor 71 at the minimum rotation number m1 has been described as an example. At this time, the tilt operation position of the operation lever 64 serving as a determination reference is not limited to the fifth operation position L5 (full lever position), and may be set to, for example, the third operation position L3 (half lever position).

  Further, in the embodiment shown in FIGS. 9 to 11, until the operation lever 64 reaches the fifth operation position L5 (time t1 to t2), the tilt operation amount of the operation lever 64 and the accelerator pedal 66 are related to the depression operation amount. Instead, the configuration for performing the control to rotate the electric motor 71 at the relatively low minimum rotational speed m1 has been described as an example. The rotation speed of the electric motor 71 at this time is not necessarily set to the relatively low minimum rotation speed m1, and is further set to a higher rotation speed (for example, rotation between the minimum rotation speed m1 and the maximum rotation speed m2). It is also possible to set to (number).

  In the above-described embodiment, the object to which the present invention is applied is a work vehicle whose tire body is a tire wheel type, but the vehicle body is not necessarily limited to a tire wheel type, and is driven by a crawler device or the like. There may be. Alternatively, it may be an orbital working vehicle that includes an orbital traveling wheel and travels on an orbital track, and further, an orbital working vehicle that includes both a tire wheel and an orbital traveling wheel.

  In the above-described embodiment, the digging column car has been described as an example of the work vehicle according to the present invention. However, the present invention is not limited to this. For example, other work such as an aerial work vehicle, a railroad vehicle, and a crane vehicle The present invention can be similarly applied to other work vehicles.

1 Drilling column car (work vehicle)
20 swivel (working device)
23 Swing motor (hydraulic actuator)
24 Rolling cylinder (hydraulic actuator)
30 Boom (Working device)
31 Telescopic cylinder (hydraulic actuator)
40 Winch device (working device)
43 Winch motor (hydraulic actuator)
50 Earth auger device (working device)
54 Auger motor (hydraulic actuator)
64 Operation lever (first operation means)
66 Accelerator pedal (second operating means)
67 Pedal depression position detector (second operation amount detection means)
71 Electric motor (first power source)
80 controller (power source control means)
101 Lever operation position detector (first operation amount detection means)
A5 Fifth operation position (second predetermined operation amount)
E engine (second power source)
L5 Fifth operation position (first predetermined operation amount)
m1 Minimum rotation speed (first predetermined rotation speed)
e1 Low speed (second predetermined speed)
V1 to V5 control valve P1 first hydraulic pump P2 second hydraulic pump

Claims (3)

A working device operated by a hydraulic actuator;
An electric motor that rotates by receiving electric power;
Engine ,
A first hydraulic pump that is driven by receiving a rotational driving force from the electric motor and supplies hydraulic oil to the hydraulic actuator;
A second hydraulic pump driven by receiving rotational driving force from the engine and supplying hydraulic oil to the hydraulic actuator;
First operating means for performing an operation for operating the working device;
A control valve for controlling the supply and discharge of hydraulic fluid from the first and second hydraulic pumps to the hydraulic actuator by changing the valve opening according to the operation performed on the first operating means;
First operation amount detection means for detecting an operation amount of the first operation means;
A second operating means for performing an operation for setting the rotational speed of the electric motor and the engine ;
Second operation amount detection means for detecting an operation amount of the second operation means;
Power source control means for controlling the drive of the electric motor and the engine based on the detection results in the first and second operation amount detection means,
The power source control means rotates the electric motor at a first predetermined rotation speed regardless of the operation amount of the second operation means when the operation amount of the first operation means is less than the first predetermined operation amount. , corresponding to the operation amount of the operation amount of the operation amount is the first predetermined operation amount or more der Ri and the second operating means of the first operating means and the second predetermined operation amount less sometimes the second operating means wherein controlling the rotation of the electric motor, the second operating means is operated beyond said second predetermined operation amount state of the operation is the first predetermined operation amount or the first operating means Te Sometimes, the engine is additionally driven, and the rotational speed of the electric motor is reduced so as to be lower than the rotational speed corresponding to the operation amount of the second operating means. The power source control means includes a hydraulic oil amount per unit time discharged from the first hydraulic pump in accordance with the amount of operation of the second operating means before the said engine is driven, the engine is driven Depending on the operation amount of the second operating means, the rotational speed of the electric motor is sometimes set so that the amount of hydraulic oil discharged from the first hydraulic pump and the second hydraulic pump per unit time is substantially the same. The work vehicle control device according to claim 1, wherein the work vehicle is lowered so as to be lower than the rotational speed. The power source control means rotates the engine at a second predetermined rotational speed when the second operation means is operated while the engine is driven, regardless of the operation amount of the second operation means. The work vehicle control device according to claim 1, wherein the rotation of the electric motor is controlled in accordance with an operation amount of the second operation means.

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