FINE OPERATION MODE CHANGE-OVER SYSTEM FOR HYRAULIC EXCAVATOR

Abstract: A hydraulic excavator adapted to be changed over simply to a fine operation mode so as to control the capacity of a hydraulic pump through load-sensing control to thereby make it possible to perform accurate work when the machine needs to be finely operated temporarily for operations such as ground levelling, and position adjustment on a dump vessel, wherein the fine operation mode is easily cleared to switch the excavator to a standard mode to thereby improve operability, as well as work efficiency. When the excavator is switched to the fine operation mode so as to control the capacity of the hydraulic pump through load-sensing control for accurate work, the engine is driven at such a torque and engine revolution as permitting a minimum fuel consumption, thus reducing the fuel consumption of the engine.

Description: Field of the Invention The present invention relates to a fine operation mode changeover system for a hydraulic excavator according to the preamble of claim 1 which is intended to enable performance of accurate operation by simply changing over the operation to a fine operation mode when fine control of operation of a working machine such as a hydraulic excavator is provisionally required, for example, in leveling of a ground and position adjustment on a dump vessel and easy cancellation of the fine operation mode of the hydraulic excavator in normal operation thereby improving operability and work efficiency of the machine Description of the Related Art When temporary fine control of the operation is required in such work as ground leveling by a hydraulic excavator or position adjustment on a dump vessel, such fine operation can be carried out with a far smaller quantity of fuel than in typical excavating work. Therefore, an engine revolution rate at a specified torque T0 is controlled to N1, N2 or N3 (rev/min) and a required quantity of fuel, that is, V.N1, V.N2 or V.N3 (cc/min), while maintaining a capacity V (cc/rev) of a hydraulic pump to be driven by the engine at a fixed level, is controlled by reducing a fuel injection quantity as shown in an engine torque graph in Fig. 8 thereby reducing fuel consumption of the engine. As well known, an absorption torque T of the hydraulic pump is denoted as T = kP × V wherein k is a proportional constant and P is a load pressure and, if the capacity V (cc/rev) of the hydraulic pump is fixed, the load pressure PO of the hydraulic pump with the absorption torque TO given in Fig.8 as the load pressure is proportional to the absorption torque TO. An oil quantity of a hydraulic pump is reduced by a method which reduces the capacity V of the hydraulic pump by fixing a fuel injection to the engine as shown in Fig. 9 (the rotation rate of the engine is approximately fixed) and changing over the operation of the working machine to the fine operation mode. However, in the case of a method for reducing the oil quantity of the hydraulic pump by decreasing the rotation rate of the engine in a state where the capacity V of the hydraulic pump is kept fixed as shown in Fig. 8, the matching points A2, A3 with the absorption torque TO corresponding to a specified load are more away from the center of the equivalent fuel consumption efficiency curve B of the engine (hereinafter referred to as the equivalent fuel consumption curve with 100% at the center) and therefore this method is disadvantageous in that the fuel consumption of the engine lowers accordingly and the operator will suffer from a great deal of fatigue in frequently repeated operation for adjusting the rotation rate of the engine during the work by the hydraulic excavator. In the method as shown in Fig. 9, assuming that k is a proportional constant and P is a load pressure, the absorption torque T of the pump is denoted as T = kP × V as described above and therefore, when the maximum torque is required, reduction of the value V with respect to the maximum load pressure P set by the relief valve will result in reduction of absorption torque of the hydraulic pump from Ts to Tl. Accordingly, this method is also disadvantageous in that the matching point with the hydraulic pump is shifted from As to Al to be more away from the center of the center of the equivalent fuel consumption curve C of the engine and therefore the fuel consumption efficiency of the engine deteriorates as much as such remoter location of the matching point, the operating valves should be controlled in a small range where the operating strokes of operating valves are small and the operability is deteriorated since only an insufficient capacity of the hydraulic pump can be obtained from the reduced absorption torque Tl f the hydraulic pump because the load sensing control is not effected. As shown in Fig. 8, frequent changeover operations of the fine operation mode and the ordinary operation mode will bring about a considerable degree of fatigue to the operator. To improve fuel consumption, achieve economic operation and lower an engine sound for reduced noise in the second embodiment of EP 0432266 A1 with the features of the first part of claim 1 is described a hydraulic driving system for construction machinery. In that construction the hydraulic system includes a group of sensors comprised of a tilting angle sensor for detecting a swash plate tilting angle of the hydraulic pump a pressure sensor for detecting the delivery pressure of the hydraulic pump, a differential pressure sensor for detecting the differential pressure between the delivery pressure of the hydraulic pump and the maximum load pressure of the actuators and a revolution sensor for detecting the revolution speed of the engine, a controller equipped with a pump control section adapted to receive and process respective detection signals from the group of those sensors and a tilting angle control device driven in response to an electric signal output from the controller. The system eliminates saturation of the pump. The EP 0228707 A1 describes a control system of hydraulic construction machinery which is capable of freely changing the operation modes suffering the disadvantages of producing noises and increasing fuel consumption and which is substantially free a variation in the quantity of pressurized fluid delivered by the hydraulic pump when the operation modes are changed. Specifically an economy mode for performing a low-load operation and a power mode for performing a high-load operation are set and selected by the mode selection switch 25 shown in a block in two-dots chain lines in Fig. 2. The mode selection switch 25 produces a power mode signal when moved to power mode selection position P and produces an economy mode signal when moved to an economy mode selection position E. The known fine operation mode changeover device for a hydraulic excavator comprises a variable capacity type hydraulic pump, an actuator to be driven by the above described hydraulic pump, an operating valve provided in a duct between the hydraulic pump and the actuator, a load sensing control unit for the hydraulic pump, a fine operation mode changeover switch, and a controller which receives a changeover signal from the fine operation mode changeover switch and outputs a differential pressure signal of upper and lower streams of the operating valve, wherein a load sensing differential pressure signal from the controller is not outputted to the load sensing control unit since the fine operation mode changeover switch is not operated when the actuator of the hydraulic excavator is driven in a routine operation mode and the differential pressure between the upper stream and the lower stream of the operating valve is controlled to be a fixed differential pressure preset in the load sensing control unit. When a changeover signal from the fine operation mode changeover switch is entered into the controller to drive the actuator of the hydraulic excavator in the fine operation mode, the load sensing differential pressure signal from the controller is outputted to the load sensing control unit so as to reduce the capacity of the hydraulic pump through the capacity control cylinder. The device also comprises a variable capacity type hydraulic pump, an engine for driving the hydraulic pump, an actuator to be driven by the hydraulic pump, an operating valve provided in a duct between the hydraulic pump and the actuator, a load sensing control unit, a fine operation mode changeover switch, and a controller which receives a changeover signal from the fine operation mode changeover switch and outputs a fuel injection quantity signal to a governor drive unit and a differential pressure signal of upper and lower streams of the operating valve, wherein a load sensing differential pressure signal from the controller is not outputted to the load sensing control unit since the fine operation mode changeover switch is not operated when the actuator of the hydraulic excavator is driven in a routine operation mode and the differential pressure between the upper stream and the lower stream of the operating valve is controlled to be a fixed high differential pressure preset in the load sensing control unit and simultaneously the horse power of the engine rises up to a preset high horse power. Accordingly, the capacity of the variable capacity type hydraulic pump increases and the rotation rate of the engine in reference to the specified torque is increased owing to the rise of the horse power and therefore the discharge per unit time of the variable capacity type hydraulic pump increases. When the fine operation mode changeover switch is operated to drive the hydraulic excavator in the fine operation mode, a low fuel injection quantity signal from the controller is outputted to the governor drive unit of the engine to reduce the horse power of the engine and the differential pressure signal which seems to reduce the differential pressure between the upper and lower streams of the operating valve for the actuator is outputted to the load sensing control valve and therefore the capacity of the variable capacity type hydraulic pump in reference to the specified amount of operation of the operating valve for the actuator reduces. Accordingly, the capacity of the variable capacity type hydraulic pump decreases and the rotation rate of the engine in reference to the specified torque is decreased owing to the reduction of the horse power and therefore the discharge per unit time of the variable capacity type hydraulic pump decreases. The load sensing control unit is adapted to decrease the capacity of the hydraulic pump through the capacity control cylinder of the hydraulic pump according to the increase of the differential pressure signal to be outputted from the controller and increase the capacity of the hydraulic pump through the capacity control cylinder of the hydraulic pump according to the decrease of the differential pressure signal. The load sensing control unit decreases the capacity of the hydraulic pump through the capacity control cylinder of the hydraulic pump when the differential signal to be outputted from the controller and increases the capacity of the hydraulic pump through the capacity control cylinder of the hydraulic pump when the differential signal decreases. The controller is adapted to output a low engine fuel setting signal from the engine fuel setter to the engine fuel signal generator by actuating the engine fuel setter and the load sensing differential pressure setter according to the changeover signal from the fine operation mode changeover switch and a low load sensing differential pressure setting signal from the load sensing differential pressure setter to the load sensing differential pressure signal generator to output a low fuel injection quantity signal from the engine fuel signal generator to the governor drive unit and a low load sensing differential pressure signal to the load sensing control unit and, when the controller receives the changeover signal from the fine operation mode changeover switch, the engine fuel setting device and the load sensing differential pressure setting device are actuated with the changeover signal. When the above described setting devices are actuated, the low engine fuel setting signal is outputted to the engine fuel signal generator and the low load sensing differential pressure setting signal is outputted to the low sensing differential pressure signal generator to output a low fuel injection quantity signal from the engine fuel signal generator to the governor drive unit of the engine and a low load sensing differential pressure signal from the load sensing differential pressure signal generator to the load sensing control unit. SUMMARY OF THE INVENTION In accordance with the present invention the fine operation mode changeover switch is adapted to be provided on the operation lever of the operating valve and the fuel consumption of the system is optimized. Since the fine operation mode changeover switch is provided on the operation lever of the operating valve, the fine operation mode or the normal operation mode can be easily selected by pushing or releasing the fine operation mode changeover switch even during operation of the working machine. The system comprises a variable capacity type hydraulic pump, an actuator to be driven by the hydraulic pump, an operating valve provided in a duct which connects the hydraulic pump and the actuator, a capacity control cylinder of the hydraulic pump, a fine operation mode changeover switch, a load sensing control unit which changes over the operation to decrease the capacity of the hydraulic pump through the capacity control cylinder owing to an increase of the difference of pilot pressures of the upper and lower streams of the operating valve, and a controller which outputs a specified electrical signal which serves to reduce the capacity of the hydraulic pump through the capacity control cylinder when a changeover signal from the fine operation mode changeover switch is entered, wherein the load sensing control unit, which uses a differential pressure of the upper and lower streams of the operating valve as a plot pressure, is controlled so that the differential pressure of the upper and lower streams of the operating valve may be maintained at a fixed level through the capacity control cylinder according to the differential pressure of the pilot pressure when the operating valve is operated by the operation lever for driving the actuator of the hydraulic excavator in a standard operation mode. When the changeover signal is entered from the fine operation mode changeover switch into the controller to drive the actuator of the hydraulic excavator in the fine operation mode, a specified electrical signal which reduces the capacity of the hydraulic pump is outputted from the controller to the load sensing control unit through the capacity control cylinder. Since the specified electrical signal to be outputted from the controller is adapted to be entered into a solenoid of a load sensing valve and reduce the capacity of the hydraulic pump through the capacity control cylinder, the specified electrical signal to be outputted from the controller is entered into the solenoid of the load sensing control unit and serves to reduce the capacity of the hydraulic pump. The device in accordance with the present invention comprises a variable capacity type hydraulic pump, an engine for driving the hydraulic pump, an actuator to be driven by the hydraulic pump, an operating valve provided in a duct which connects the hydraulic pump and the actuator, a load sensing control unit of the hydraulic pump, a capacity sensor of the hydraulic pump, a rotation rate sensor of the engine, a hydraulic pressure sensor of the actuator, and a fine operation mode changeover switch and further comprises a controller which receives the signals of the capacity sensor, the rotation rate sensor of the engine and the hydraulic pressure sensor of the actuator, calculates a control signal according to which the engine is driven with the minimum fuel consumption at the specified horse power designated by the fine operation mode changeover switch and outputs this control signal to the load sensing control unit and the governor drive unit of the engine, wherein the capacity of the variable capacity type hydraulic pump can be reduced for the same operation amount of the operation lever by calculating the control signal according to which the engine is driven with the minimum fuel consumption at the specified horse power for the fine operation mode stored in the controller, changing over the load sensing control unit according to the control signal and reducing the capacity of the hydraulic pump through the capacity control cylinder when the changeover signal from the fine operation mode changeover switch is entered into the controller to drive the actuator of the hydraulic excavator in the fine operation mode, and the engine can be operated with the minimum fuel consumption for the horse power reduced by outputting the control signal to the governor drive unit of the engine. The control signal with which the engine is operated with the minimum fuel consumption is set according to an engine torque and an engine rotation rate which provide the minimum fuel consumption on the equivalent horse power curve of the engine and therefore the engine is operated with the engine torque and the engine rotation rate which provide the minimum fuel consumption on the equivalent horse power curve. The fine operation mode changeover switch is provided on the operation lever of the actuator to permit easy changing over of the fine operation mode and the standard operation mode by pushing and releasing the fine operation mode changeover switch even during operation of the working machine. Thus the following effects can be obtained from the present invention. (1) A plurality of operation modes are available by changing over the operation mode. In any operation mode, a required flow rate can be ensured and the engine can be operated with the minimum fuel consumption since the rotation rate of the engine can be set independently of adjustment of the capacity of the hydraulic pump by adjusting the capacity of the hydraulic pump according to the load sensing control. (2) The operability by the operator can be improved by load sensing control of the capacity of the hydraulic pump so as to operate the operating valve in a wide range. (3) A mode suited for the work can be selected by a simple operation such as mere touching of the fine operation mode changeover switch provided on the operation lever to perform highly accurate operation of the working machine and the work efficiency can be improved by operating the actuator at a high speed since the operation is immediately changed over to the normal operation mode when the fine operation mode changeover switch is released. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a diagram showing a control circuit which is not claimed but illustrates the technical field of the invention; Fig. 2 is a diagram showing another control circuit which is also not claimed but illustrates the technical field of the invention; Fig. 3 is a diagram showing the details of the controller shown in Fig. 2; Fig. 4 is a diagram showing a control circuit according to an embodiment of the present invention; Fig. 5 is a diagram showing the details of the controller shown in Fig. 4; Fig. 6 is a diagram showing equivalent fuel consumption and equivalent horse power curve on the torque T - rotation rate N plane f the engine common to the embodiment of the present invention; Fig. 7 is a diagram showing an equivalent absorption torque curve on the hydraulic pressure P - capacity V plane of the hydraulic pump common to the embodiment of the present invention; Fig. 8 is a diagram showing the engine torque curve when the fuel injection quantity is varied in the prior art; and Fig. 9 is a diagram showing the engine torque curve when the capacity of the hydraulic pump is varied while the fuel injection quantity is kept constant in the prior art. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS In Fig. 1 reference number, 1 is an engine, 2 is a hydraulic pump to be driven by the engine 1, 3 is an actuator of a working machine, 4 is an operating valve provided in ducts 5a, 5b which connect the hydraulic pump 2 and the actuator 3 of the working machine, 6 is a pilot operating valve for operating the operating valve 4, 6a is an operation lever of the pilot operating valve 6, 7 is a capacity control cylinder for driving a diagonal plate 2a of the hydraulic pump 2, 7a is a spring provided in a bottom chamber 7b of the capacity control cylinder 7 to energize a piston 7d in a direction toward a rod chamber 7c, 7e is a piston rod for coupling the piston 7d to the diagonal plate 2a, 8 is a load sensing control unit for changing over the control pressure of the capacity control cylinder 7, 8a is a solenoid of a load sensing valve 8 connected to a controller 15, 8b is a pilot cylinder of the load sensing valve 8 connected to an upper stream duct 5a of the operating valve 4, 8c is a plot cylinder of the load sensing control unit 8 connected to a lower stream duct 5b of the operating valve 4, 8d is a differential pressure setting spring of a load sensing valve 8, 9 is a control pump as a control pressure source of the capacity control cylinder 7, 10 is a power source, 11 is a fine operation mode changeover switch, 11a is a return spring of the fine operation mode changeover switch 11, 12 is a magnet, 13 is a spring, 14 is a changeover switch, and 15 is a controller which enters a changeover signal from the changeover switch 14 and outputs a differential pressure signal ip of upper and lower streams of the operating valve 4 to the solenoid 8a of the load sensing control unit 8. The controller 15 comprises a load sensing differential pressure setter 16 and a load sensing differential pressure signal generator 17. 23 is a tank. An operation of a configuration shown in Fig. 1 is described below. In an operation of the hydraulic excavator in a normal operation mode, the voltage of the power supply 110 is not applied to the magnet 12 since the fine operation mode changeover switch 11 is not pressed and therefore the magnet 12 is demagnetized and the changeover switch 14 is connected with the contact A by the spring 13. Accordingly, the voltage of the power supply 10 is not applied to the load sensing differential pressure setter 16 in the controller 15 and therefore the load sensing differential pressure signal ip is not outputted from the load sensing differential pressure signal generator 17 to the solenoid 8 of the load sensing control unit 8. Accordingly, the load sensing control unit 8 operates to provide a high load sensing differential pressure which is determined by a preset spring 8d. As described above, since the operation in a normal operation mode is carried out with a high rotation rate of the engine and a high capacity of the hydraulic pump, the discharge of the hydraulic pump per unit time increases and the actuators can be operated at high speeds to improve the working efficiency. For changing over the operation to the fine operation mode during the normal operation mode, the voltage of the power supply 10 is applied to the magnet 12 and the changeover switch 4 is connected to the contact B when the fine operation mode changeover switch 11 is pressed. The voltage of the power supply 10 is applied to the load sensing differential pressure setter 16 in the controller 15 and, when a low load sensing differential pressure setting signal Δ Pb is outputted from the load sensing differential pressure setter 16 to the load sensing differential pressure signal generator 17, the load sensing differential pressure signal generator 17 , which serves as a decreasing function generator, outputs the load sensing differential pressure signal ip corresponding to the low load sensing differential pressure setting signal Δ Pb to the solenoid 8a of the load sensing control unit 8 and therefore the capacity of the hydraulic pump 2 is reduced for the same operation amount of the operating valve 4. Since the discharge of the hydraulic pump 2 per unit time decreases as described above even though the rotation of the engine is constant, fine operation will be easy. In this first embodiment, the device is simplified in its construction and the operating valve can be controlled in a wide range of operation and it is therefore advantageous in that the operability can be improved and the changeover of the modes is easy. However, the measures for reducing fuel consumption of the engine have not been taken. In Figs. 2 and 3 showing an other embodiment, the descriptions of the configurations and operations of 1∼14, 16, 17 and 23 in Fig. 2 are omitted because of being the same as in Fig. 1. 20 is a controller which comprises the load sensing differential pressure setter 16, the load sensing differential pressure signal generator 17, the engine fuel setter 18 and the engine fuel signal generator 19, receives the changeover signal from the fine operation mode changeover switch 11, outputs the differential pressure signal ip of upper and lower streams of the operating valve 4 to the solenoid 8 of the load sensing control unit 8 and outputs the fuel injection quantity signal ih to the governor drive unit 1a of the engine 1. The following describes the operation of the configuration shown in Figs. 2 and 3. In Fig. 2, the fine operation mode changeover switch 11 is not pressed in operation of the hydraulic excavator in the normal operation mode and the voltage of then power supply 10 is not applied to the magnet 12; therefore the magnet 12 is demagnetized and the changeover switch 14 is forced to connect to the contact A by the spring 13. Accordingly, the voltage of the power supply 10 is not applied to the load sensing differential pressure setter 16 in the controller 15 and therefore the load sensing differential pressure signal ip from the 10a sensing differential pressure signal generator 17 is not outputted to the solenoid 8a of the load sensing control unit 8 and the fuel injection quantity signal ih from the engine fuel signal generator 19 is not outputted to the governor drive unit 1a of the engine 1. Accordingly, the load sensing control valve 8 provides a high load sensing differential pressure which is determined by the preset spring 8d and the governor dive unit 1a of the engine 1 is operated with a preset high fuel injection quantity. As described above, since the operation in a normal operation mode is carried out with a high rotation rate of the engine and a high capacity of the hydraulic pump, the discharge of the hydraulic pump per unit time increases and the actuators can be operated at high speeds to improve the working efficiency. For changing over the operation to the fine operation mode during the normal operation mode, the voltage of the power supply 10 is applied to the magnet 12 and the changeover switch 4 is connected to the contact B when the fine operation mode changeover switch 11 is pressed. The voltage of the power supply 10 is applied to the load sensing differential pressure setter 16 in the controller 20 and, when a low load sensing differential pressure setting signal Δ Pb is outputted from the load sensing differential pressure setter 16 to the load sensing differential pressure signal generator 17, the load sensing differential pressure signal generator 17 , which serves as a decreasing function generator, outputs the load sensing differential pressure signal ip corresponding to the low load sensing differential pressure setting signal Δ Pb to the solenoid 8a of the load sensing control unit 8 and therefore the capacity of the hydraulic pump 2 is reduced for the same operation amount of the operating valve 4. Since the voltage of the power supply 10 is applied to the engine fuel setter 18 in the controller 20, when a low engine fuel setting signal Hb from the engine fuel setter 18 is outputted to the engine fuel signal generator 19, the engine fuel signal generator 19, which serves as an increasing function generator, outputs a low engine fuel signal ih corresponding to the low engine fuel setting signal Hb to the governor drive unit 1a of the engine 1 and the rotation rate of the engine is reduced. As described above, the operation is carried out with a low rotation rate of the engine and a low capacity pf the hydraulic pump in the fine operation mode and therefore the discharge of the hydraulic pump 2 per unit time decreases and fine operation can be easily carried out. In Figs. 4 and 5 showing an embodiment of the present invention, the descriptions of the configuration and operations of 1∼14 and 23 in Fig. 4 are omitted because of being the same as in Fig. 1. 21 is a hydraulic sensor for converting a hydraulic pressure of a lower stream duct 5b of the operating valve 4 to an electrical signal, 31 is a pump capacity sensor for detecting the capacity of the hydraulic pump 2, 3 is an engine rotation rate sensor for detecting a rotation rate of the engine 1, and 30 is a controller which receives the detection signals and the command signals from the hydraulic sensor 21 of the actuator 3, the operation mode changeover switch 11, the pump capacity sensor 31 of the hydraulic pump 2 and the engine rotation rate sensor 32 of the engine 1, calculates the control signals iN and iV according to which the engine 1 is operated with the minimum fuel consumption and the specified horse power assigned by the operation mode changeover switch 11 and outputs them control signal iN to the governor drive unit 1a of the engine 1 and the control signal iV to the solenoid 8a of the load sensing valve 8. This controller 30 includes a target value setter 22 for setting a target engine rotation rate NS and a target engine torque TS for the standard operation mode, a capacity difference calculator 24 for calculating a difference Δ VS between the target capacity VS calculated from the target engine torque TS and a detection value P of the hydraulic sensor 21 and a detection value V of the capacity sensor 31, and an engine rotation rate difference calculator 25 for calculating a difference Δ NS between the target engine rotation rate NS and an actual engine rotation rate N detected by the engine rotation rate sensor 32. Similarly for the fine operation mode, the controller 30 includes a target value setter 23 for setting a target engine rotation rate NB and a target engine torque TB for the fine operation mode, a capacity difference calculator 26 for calculating a difference Δ VB between the target capacity VB calculated from the target engine torque TB and a detection value P of the hydraulic sensor 21 and a detection value V of the capacity sensor 31, and an engine rotation rate difference calculator 27 for calculating a difference Δ NB between the target engine rotation rate NB and an actual engine rotation rate N detected by the engine rotation rate sensor 32. In addition, the controller 30 includes a control signal generator 28 for converting the capacity difference signal Δ VS or Δ VB to a control signal iv to be applied to the solenoid 8a and a control signal generator 29 for converting the engine rotation rate difference signal Δ NS or Δ NB to a control signal iN to be applied to the governor drive unit 1a. An operation of a configuration shown in Figs. 4 and 5 is described below. For operation of the hydraulic excavator in the standard operation mode, the changeover switch 14 is connected to the contact A unless the fine operation mode changeover switch 11 is pressed, and the target engine rotation rat NS and the target engine torque TS and the detection value P of the hydraulic sensor are entered into the capacity difference calculator 24 by the target value setter 22 in the controller 30. As well known, assuming that k is a proportional constant, the target engine torque TS can be denoted as TS = kPVS and therefore the target pump capacity VS is calculated and the difference Δ VS between the target pump capacity VS and the detection value V of the pump capacity sensor 31 is calculated. When the signal of the capacity difference Δ VS is outputted to the control signal generator 28, the control signal iv corresponding to the capacity difference signal Δ VS as shown is outputted to the solenoid 8a of the load sensing valve 8. If the capacity difference signal Δ VS is small in the control signal generator 28, the control signal iv is set to have a large value. For example, if the actual pump capacity V to be detected by the pump capacity sensor 31 is excessively large for the target pump capacity VS, the capacity difference signal Δ VS becomes small and the control signal iv becomes large and therefore the energizing force of the solenoid 8a which pushes the load sensing valve 8 rightwardly becomes large. Accordingly, the control pressure of the control pump 9 is supplied to the bottom chamber 7b of the capacity control cylinder 7, and a piston rod 7e of the capacity control cylinder 7 moves to the right side to control the diagonal plate 2a of the variable capacity type hydraulic pump 2 in a direction where the capacity is decreased. Thus the capacity is controlled so that the capacity difference signal Δ VS is 0, that is, the actual pump capacity V becomes the target pump capacity VS. Similarly, when the target engine rotation rate NS set by the target value setter 22 and the actual engine rotation rate N detected from the engine rotation rate sensor 32 are entered into the engine rotation rate difference calculator 25, a difference Δ NS between the target engine rotation rate NS and the actual engine rotation rate N detected by the engine rotation rate sensor 32. If the engine rotation rate difference signal Δ NS is small in the control signal generator 29, the control signal iN is set to have also a small value. For example, if the actual engine rotation rate N detected by the engine rotation rate sensor 32 is excessively small for the target engine rotation rate NS, the engine rotation rate difference signal Δ NS and also the control signal iN become to have a large value; therefore, the capacity is controlled so that the governor drive unit moves to a larger stroke to cause the fuel to be more injected and the engine rotation rate N to increase and the engine rotation rate difference signal Δ NS becomes 0, that is, the actual engine rotation rate N becomes the target engine rotation rate NS, and excavation work can be carried out the target engine rotation rate NS and the target engine torque TS with which the minimum fuel consumption can be achieved. For operation of the hydraulic excavator in the fine operation mode, the changeover switch 14 is connected to the contact B when the fine operation mode changeover switch 11 is pressed and the target engine rotation rate NB and the target engine torque TB are set by the target setter 23 in the controller 30 and the excavation work in the fine operation mode can be carried out, as in the standard operation mode, with the target engine rotation rate NB and the target engine torque TB with which the minimum fuel consumption can be achieved. For changing over the operation to the standard operation mode during the fine operation mode, the fine operation mode changeover switch 11 which is kept depressed should be released. Then the changeover switch 14 is changed over to the contact A and the machine can be immediately released from the fine operation mode and changed over to the standard operation mode. Fig. 6 shows an equivalent horse power curve and an equivalent fuel consumption curve which are drawn on the torque T - the rotation rate N plane of the engine wherein A denotes the equivalent horse power curve with the fuel consumption of 100% at the center thereof. HPS denotes the equivalent horse power curve in the standard operation mode, HPB denotes the equivalent horse power curve in the fine operation mode, and TS and TB respectively denote the engine torque on equivalent horse power curves HPS and HPB where the minimum fuel consumption is achieved. Fig. 7 is a diagram showing an equivalent torque curve drawn on the hydraulic pressure P - the capacity V plane of the hydraulic pump to be driven by the above described engine wherein TS and TB are respectively absorption torques of the hydraulic pump corresponding to the engine torques TS and TB shown in Fig. 6. The present invention is to provide a useful fine operation changeover device for a hydraulic excavator, capable of enabling to carry out accurate work, for example, ground leveling or position adjustment on a dump vessel, while simply changing over a working machine such as a hydraulic excavator to the fine operation mode which is temporarily required, and improving operability and work efficiency by easily canceling the fine operation mode in the standard operation mode.

Claims: A fine operation mode changeover system for a hydraulic excavator comprising a variable capacity type hydraulic pump (2), an engine (1) driving said hydraulic pump, during operation, an actuator (3) to be driven by said hydraulic pump, an operating valve (4) provided in a conduit between said hydraulic pump and said actuator, a load sensing control unit (8) of said hydraulic pump, a capacity sensor (31) of said hydraulic pump, a rotation sensor (32) of said engine, a hydraulic pressure sensor (21) of said actuator, a mode changeover device (11) and a controller (30) which inputs respective signals from said capacity sensor (31), said rotation sensor (32) and said hydraulic pressure sensor (21), calculates control signals (iV, iN) and outputs said control signals to both said load sensing control unit (8) and a governer drive unit (1a ) of the engine during operation., characterized in that the mode changeover device is a fine operation mode changeover switch (11) provided on an operation lever (6a) of said actuator (3) so as to select easily a fine operation mode or a normal operation mode even in operation of the hydraulic excavator according to which said engine (1) is operated with the minimum fuel consumption on an equivalent horse power courve (HP S ,HP B ) designated by one of said two modes of said fine operation mode changeover switch (11). A fine operation mode changeover system for a hydraulic excavator in accordance with claim 1, wherein said control signals (iV, iN) according to which said engine (1) is operated with the minimum fuel consumption are determined by the combination of an engine torque (T S , T B ) and an engine rotation rate (N S , N B ) which represent the minimum fuel consumption on the equivalent horse power curve of the engine, for each of the two switch modes in the respective engine torque versus engine rotation diagram (Fig.6).

Inventors: TAKAMURA FUJITOSHI, TAKAMURA, FUJITOSHI
Applicants: KOMATSU MFG CO LTD, KABUSHIKI KAISHA KOMATSU SEISAKUSHO
Application year: 1992
Main classification: E02F9
IPC codes: E02F9