JP2021095950A - Hydraulic circuit for construction machinery - Google Patents

Abstract

To provide a hydraulic circuit for construction machinery having a split flow type variable capacity pump subjected to negative control, capable of assuring smooth runability even if manipulation amounts for left and right travel motors are different.SOLUTION: A hydraulic circuit 5 includes an integrated controller 7 for controlling a discharge amount of a variable capacity pump 51 by a hydraulic signal according to negative control pressure, and a pressure sensor 53d for a travel detection for transmitting a travel detection signal. Breed-off openings of direction switching valves 55e and 55f for traveling have an opening characteristic corresponding to a maximum discharge amount of the variable capacity pump 51 at start of driving travel motors 22a and 22b. Breed-off openings of direction switching valves 55a and 55b for a working machine have an opening characteristic corresponding to the discharge amount of the variable capacity pump 51 controlled based on the negative control pressure. The integrated controller 7 causes the charging amount of the variable capacity pump 51 to become maximum by cutting off the hydraulic signal if the travel detection signal is inputted.SELECTED DRAWING: Figure 2

Description

The present invention relates to a hydraulic circuit of a construction machine.

Patent Document 1 below discloses a hydraulic circuit of a construction machine having a split flow type variable displacement pump that is negatively controlled (hereinafter, also referred to as negative control control).

In the hydraulic circuit of Patent Document 1, when a slow turn is performed in which one of the left and right crawlers is operated with a large operation and the other crawler is operated with a small operation with respect to the traveling direction, the direction switching valve of the traveling motor of the crawler with the small operation is performed. A large amount of pressure oil tries to bleed into the bleed-off opening, but with the characteristics of the bleed-off opening optimized for negative control, the pressure in the circuit rises without proper bleeding, and to prevent engine stall. In addition, the function of reducing the discharge amount of the variable-capacity pump works, causing a problem that the traveling speed of the traveling motor of the crawler that has performed a large operation drops sharply.

Japanese Unexamined Patent Publication No. 2012-233551

Therefore, in view of the above problems, the present invention is a hydraulic circuit of a construction machine having a split flow type variable displacement pump controlled by a negative controller, and provides smooth running performance even when the amount of operation to the left and right traveling motors is different. The purpose is to provide a hydraulic circuit for construction machinery that can be secured.

The hydraulic circuit of the construction machine of the present invention includes a split flow type variable capacity pump having a first discharge port and a second discharge port, and a first traveling motor driven by pressure oil discharged from the variable capacity pump. 2 Travel motor, 1st working machine actuator, 2nd working machine actuator, 1st center bypass oil passage from the 1st discharge port to the oil tank, and 2nd center bypass from the 2nd discharge port to the oil tank. Of the oil passage, the first negative pump throttle and the second negative pump throttle arranged at the most downstream of the first center bypass oil passage and the second center bypass oil passage, and the first negative pump throttle and the second negative pump throttle, respectively. An output means that outputs the smaller pressure of the upstream pressure as a negative pressure, a control device that controls the discharge amount of the variable displacement pump by a hydraulic signal corresponding to the negative pressure, and a control device.
A first traveling direction switching valve arranged in the first center bypass oil passage and controlling the first traveling motor, and a second traveling vehicle arranged in the second center bypass oil passage and controlling the second traveling motor. The directional control valve, the directional control valve for the first working machine arranged in the first center bypass oil passage and controlling the first working machine actuator, and the second center bypass oil passage arranged in the second center bypass oil passage. A directional control valve for the second work machine that controls the work machine actuator,
The first traveling operation lever for operating the first traveling direction switching valve, the second traveling operating lever for operating the second traveling direction switching valve, and the first working machine direction switching valve are provided. A first work operation lever for operating, a second work operation lever for operating the directional control valve for the second work machine, and the like.
A travel detection means for detecting that at least one of the first travel motor and the second travel motor is being driven and transmitting a travel detection signal is provided.
The bleed-off openings of the first traveling direction switching valve and the second traveling direction switching valve are such that the operating amounts of the first traveling operating lever and the second traveling operating lever reach predetermined values and the first traveling motor And has an opening characteristic corresponding to the maximum discharge amount of the variable displacement pump when the second traveling motor starts driving.
The bleed-off openings of the directional switching valve for the first working machine and the directional switching valve for the second working machine have opening characteristics corresponding to the discharge amount of the variable displacement pump controlled based on the negative control pressure.
When the travel detection signal is input, the control device shuts off the hydraulic signal to maximize the discharge amount of the variable capacitance pump.

According to the present invention, in the hydraulic circuit of a construction machine having a split flow type variable displacement pump controlled by a negative controller, even if the amount of operation to the left and right traveling motors is different, the first traveling direction switching valve and The bleed-off opening of the second traveling direction switching valve is variable when the operating amount of the first traveling operation lever and the second traveling operation lever reaches a predetermined value and the first traveling motor and the second traveling motor start driving. Since it has an opening characteristic corresponding to the maximum discharge amount of the capacity pump, the operation amount of the travel operation lever can be increased even when the negative control is cut off at the time of travel detection and the discharge amount of the variable capacity pump is maximized. An appropriate amount of pressure oil can be bleeded from the bleed-off opening of the smaller first traveling direction switching valve or the second traveling direction switching valve, and the first traveling direction switching valve or the second traveling direction switching valve can be used. It is possible to suppress the occurrence of abnormal pressurization and prevent a sudden decrease in the traveling speed of the traveling motor having a larger operating amount of the traveling operation lever. As a result, smooth running performance can be ensured.

Side view showing the hydraulic excavator according to this embodiment The figure which shows the hydraulic circuit of the hydraulic excavator which concerns on this embodiment. The figure which shows the opening characteristic of the bleed-off opening of the 1st traveling directional control valve and the 1st working machine directional switching valve.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[Structure of hydraulic excavator]
First, the schematic structure of the hydraulic excavator 1 as an example of a construction machine will be described with reference to FIG.

The lower traveling body 2 is driven by receiving power from the engine 42 to drive the hydraulic excavator 1. The lower traveling body 2 includes a pair of left and right crawlers 21 and 21 and a pair of left and right traveling motors 22 and 22 (the right traveling motor 22 is not shown in FIG. 1). The left and right traveling motors 22, 22 which are hydraulic motors drive the left and right crawlers 21 and 21, respectively, so that the hydraulic excavator 1 can move forward and backward. Further, the lower traveling body 2 is provided with a blade 23 and a blade lift cylinder 24 which is a hydraulic actuator for rotating the blade 23 in the vertical direction.

The work machine 3 is driven by receiving power from the engine 42 to perform excavation work such as earth and sand. The work machine 3 includes a boom 31, an arm 32, and a bucket 33, and by driving these independently, excavation work is possible. The boom 31, arm 32, and bucket 33 correspond to working portions, respectively, and the hydraulic excavator 1 has a plurality of working portions.

The boom 31 is rotated by a boom cylinder 31a whose base end is supported by the front portion of the upper swing body 4 and which can be expanded and contracted. Further, the arm 32 is rotated by an arm cylinder 32a whose base end portion is supported by the tip end portion of the boom 31 and which can be expanded and contracted. Then, the bucket 33 is rotated by a bucket cylinder 33a whose base end portion is supported by the tip end portion of the arm 32 and which can be expanded and contracted. The boom cylinder 31a, arm cylinder 32a, and bucket cylinder 33a correspond to a hydraulic actuator that drives a working unit.

The bucket 33 is a container-shaped member provided at the tip of the work machine 3 and provided with claws for performing excavation work. The bucket 33 is rotatably attached to the tip of the arm 32 via a pin 34. Further, the bucket 33 is connected to the bucket cylinder 33a via a link mechanism 35.

The upper swivel body 4 is configured to be swivelable with respect to the lower traveling body 2 via a swivel bearing (not shown). A control unit 41, an engine 42, a swivel base 43, a swivel motor 44, and the like are arranged on the upper swivel body 4. The upper swing body 4 swivels via the swivel bearing by the driving force of the swivel motor 44, which is a hydraulic motor. Further, the upper swing body 4 is provided with a plurality of hydraulic pumps (not shown in FIG. 1) driven by the engine 42. These hydraulic pumps supply pressure oil to the traveling motors 22, 22, the swivel motor 44, the blade lift cylinder 24, the boom cylinder 31a, the arm cylinder 32a, the bucket cylinder 33a, and the like.

A cockpit 411 is arranged in the cockpit 41. A pair of work operation levers 421 and 412 are arranged on the left and right sides of the driver's seat 411, and a pair of travel operation levers 413 and 413 are arranged in front of the driver's seat 411. The operator controls the engine 42, each hydraulic motor, each hydraulic actuator, etc. by sitting on the driver's seat 411 and operating the work operation levers 421, 412, the travel operation levers 413, 413, etc., and travels and turns. , Work, etc. can be performed.

Further, the hydraulic excavator 1 has an integrated controller 7 (not shown in FIG. 1) as a control device. The integrated controller 7 controls the control system of the hydraulic excavator 1 and outputs the control instruction to the hydraulic pump and the control instruction to the engine 42 described above.

[Flood circuit configuration]
The hydraulic circuit 5 included in the hydraulic excavator 1 will be described with reference to FIG. The hydraulic circuit 5 includes a first traveling motor 22a, a second traveling motor 22b (either a left traveling motor 22 or a right traveling motor 22), a first working machine actuator 30a, a second working machine actuator 30b, and a third working machine actuator. It has 30c (any of boom cylinder 31a, arm cylinder 32a, bucket cylinder 33a), a blade lift cylinder 24, a swivel motor 44, a variable displacement pump 51, a fixed capacitance pump 52, and a pilot pump 53.

The variable displacement pump 51 and the fixed capacitance pump 52 are driven by the engine 42, and the hydraulic actuators (first traveling motor 22a, second traveling motor 22b, first working machine actuator 30a, second working machine actuator 30b, third working machine). The pressure oil supplied to the actuator 30c, the blade lift cylinder 24, and the swivel motor 44) is discharged. The variable displacement pump 51 supplies pressure oil to the first traveling motor 22a, the second traveling motor 22b, the first working machine actuator 30a, the second working machine actuator 30b, the third working machine actuator 30c, and the blade lift cylinder 24. Drive. The fixed capacity pump 52 is driven by supplying pressure oil to the swivel motor 44.

The variable displacement pump 51 can control the discharge amount of pressure oil by changing the inclination angle of the movable swash plate 51b by driving the pump regulator 51a. The pump regulator 51a is driven by the pressure of the pilot oil (pilot pressure) discharged from the pilot pump 53.

An electromagnetic proportional valve 51c for controlling the pump regulator 51a is provided in the oil passage 53a between the pump regulator 51a and the pilot pump 53. The electromagnetic proportional valve 51c can regulate the pressure signal (pilot signal pressure) input to the pump regulator 51a by a control command from the integrated controller 7.

The variable displacement pump 51 is a so-called split flow type hydraulic pump having a first discharge port P1 and a second discharge port P2. The pressure oil discharged from the first discharge port P1 is supplied to the first traveling direction switching valve 55e and the first working machine direction switching valve 55a described later via the first center bypass oil passage 51d, and is supplied to the second discharge. The pressure oil discharged from the port P2 passes through the second center bypass oil passage 51e to the second traveling direction switching valve 55f, the second working machine direction switching valve 55b, and the third working machine direction switching valve 55c, which will be described later. , And the blade direction switching valve 55d.

A first negative control throttle 51f is provided at the most downstream of the first center bypass oil passage 51d. The first negative control throttle 51f limits the flow of pressure oil flowing through the first center bypass oil passage 51d to generate a first negative control pressure upstream of the first negative control throttle 51f. Similarly, a second negative control throttle 51 g is provided at the most downstream of the second center bypass oil passage 51e. The second negative control throttle 51g limits the flow of the pressure oil flowing through the second center bypass oil passage 51e to generate a second negative control pressure upstream of the second negative control throttle 51g.

The low-pressure selection valve 51j (corresponding to the output means) is a valve that selects and outputs a low-pressure pressure oil from the pressure oils flowing in each of the first center bypass oil passage 51d and the second center bypass oil passage 51e. The low pressure selection valve 51j has three ports 511,512,513, the first port 511 is connected to the first center bypass oil passage 51d, and the second port 512 is connected to the second center bypass oil passage 51e. Has been done. The third port 513 is connected to the negative control pressure sensor 51k. The low pressure selection valve 51j can be switched to a plurality of positions by sliding the spool 514. The spool 514 receives the first negative control pressure and the second negative control pressure so as to oppose each other, and changes the position according to the differential pressure between the first negative control pressure and the second negative control pressure.

Specifically, when the first negative control pressure and the second negative control pressure are the same, the spool 514 is held in the neutral position shown in FIG. 2 by the urging force of the spring. In the neutral position, all three ports 511, 512, 513 communicate with each other, and the negative control pressure sensor 51k detects a pressure corresponding to the average of the first negative control pressure and the second negative control pressure.

On the other hand, when the first negative control pressure is lower than the second negative control pressure, the spool 514 moves to the left in FIG. At this position, the second center bypass oil passage 51e is cut off, and the first center bypass oil passage 51d is connected to the negative control pressure sensor 51k. As a result, the negative control pressure sensor 51k detects the first negative control pressure on the low pressure side of the first negative control pressure and the second negative control pressure. Further, when the second negative control pressure is lower than the first negative control pressure, the spool 514 moves to the right in FIG. At this position, the first center bypass oil passage 51d is cut off, and the second center bypass oil passage 51e is connected to the negative control pressure sensor 51k. As a result, the negative control pressure sensor 51k detects the second negative control pressure on the low pressure side of the first negative control pressure and the second negative control pressure. As described above, the negative control pressure sensor 51k detects the negative control pressure on the low pressure side of the first negative control pressure and the second negative control pressure, converts the detected value into an electric signal, and converts the detected value into an electric signal to the integrated controller 7 as an electric negative control signal pressure. Output to.

The first negative control relief valve 51m is arranged in parallel with the first negative control throttle 51f. The first negative control relief valve 51m uses the pressure oil of the first center bypass oil passage 51d as an oil tank when the pressure of the first center bypass oil passage 51d on the upstream side of the first negative control throttle 51f exceeds a predetermined relief pressure. Miss to. As a result, when the first negative control pressure upstream of the first negative control throttle 51f becomes equal to or higher than the preset relief pressure, the first negative control relief valve 51m discharges the pressure oil to the oil tank and the first negative control pressure. Can be controlled to less than the applied relief pressure.

Similarly, the second negative control relief valve 51n is arranged in parallel with the second negative control throttle 51g, and when the second negative control pressure upstream of the second negative control throttle 51g becomes equal to or higher than the preset relief pressure, The pressure oil can be discharged to the oil tank and the second negative control pressure can be controlled to be less than the applied relief pressure.

The pressure oil discharged from the fixed capacity pump 52 is supplied to the turning direction switching valve 55g, which will be described later, via the third center bypass oil passage 52a.

Compatible with hydraulic actuators (first working machine actuator 30a, second working machine actuator 30b, third working machine actuator 30c, blade lift cylinder 24, first traveling motor 22a, second traveling motor 22b, swivel motor 44), respectively. The direction switching valve 55 is provided, and the direction switching valve 55 is a pilot type direction switching valve capable of switching the direction and capacity of the pressure oil pumped from the variable capacity pump 51 and the fixed capacity pump 52 to the hydraulic actuator. The directional control valve 55 can be switched to a plurality of positions by sliding the spool. When no pilot signal pressure is applied to either of the two pilot ports of the directional control valve 55, the directional control valve 55 is held in the neutral position by the urging force of the spring. When the direction switching valve 55 is in the neutral position, the pressure oil is not supplied to the corresponding hydraulic actuator and passes through the first center bypass oil passage 51d, the second center bypass oil passage 51e, and the third center bypass oil passage 52a. Flows into the oil tank. On the other hand, when a pilot signal pressure is applied to any of the pilot ports of the directional control valve 55, the directional control valve 55 is switched from the neutral position to another position, and the pressure oil is supplied to the corresponding hydraulic actuator. ..

In the present embodiment, the first working machine direction switching valve 55a corresponding to the first working machine actuator 30a, the second working machine direction switching valve 55b corresponding to the second working machine actuator 30b, and the third working machine actuator 30c. The third working machine direction switching valve 55c corresponding to the above, the blade direction switching valve 55d corresponding to the blade lift cylinder 24, the first traveling direction switching valve 55e corresponding to the first traveling motor 22a, and the second traveling motor 22b. The corresponding second traveling direction switching valve 55f and the swivel direction switching valve 55g corresponding to the swivel motor 44 are provided. These directional control valves are collectively called control valves.

The pilot pump 53 mainly discharges pilot oil as a command input to the directional control valve 55. However, FIG. 2 does not show the oil passage from the pilot pump 53 to the directional control valve 55. The pilot pump 53 is driven by the engine 42 and discharges pressure oil to generate a pilot signal pressure in the oil passage 53a.

Further, the hydraulic circuit 5 includes a pair of work operation levers 421 and 412 (corresponding to the first work operation lever and the second work operation lever) and a pair of travel operation levers 413 and 413 (first travel operation lever and second). (Corresponding to the traveling operation lever) is connected. The first work operation lever is mainly for operating the first work machine actuator 30a, and is a remote control valve for switching the direction and pressure of the pilot pressure oil supplied to the direction switching valve 55a for the first work machine. Have. The second work operation lever is mainly for operating the second work machine actuator 30b, and is a remote control valve for switching the direction and pressure of the pilot pressure oil supplied to the direction switching valve 55b for the second work machine. Have. Further, the first traveling operation lever is for operating the first traveling motor 22a, and has a remote control valve for switching the direction and pressure of the pilot pressure oil supplied to the first traveling direction switching valve 55e. .. The second traveling operation lever is for operating the second traveling motor 22b, and has a remote control valve for switching the direction and pressure of the pilot pressure oil supplied to the second traveling direction switching valve 55f.

The oil passage 53a between the pilot pump 53 and the pump regulator 51a is branched into a traveling detection oil passage 53b. The travel detection oil passage 53b is the first travel detection direction that moves in conjunction with the second travel detection direction switching valve 56f that moves in conjunction with the second travel direction switching valve 55f and the first travel direction switching valve 55e. It reaches the oil tank through the switching valve 56e.

The first traveling direction switching valve 56e is integrated with the first traveling direction switching valve 55e and moves in conjunction with the first traveling direction switching valve 55e. The first travel detection direction switching valve 56e can be switched to a plurality of positions by sliding the spool. When the first traveling direction switching valve 55e is held in the neutral position, the first traveling direction switching valve 56e is also held in the neutral position. When the first traveling direction switching valve 55e is switched from the neutral position to another position, the first traveling direction switching valve 56e is also switched from the neutral position to another position in conjunction with this.

When the first travel detection direction switching valve 56e is in the neutral position, the first travel detection direction switching valve 56e does not block the travel detection oil passage 53b. Therefore, the pressure oil can be distributed through the travel detection oil passage 53b. On the other hand, when the first travel detection direction switching valve 56e is in a position other than the neutral position, the first travel detection direction switching valve 56e shuts off the travel detection oil passage 53b. Similarly, the second travel detection direction switching valve 56f can be switched to a communication position for communicating the travel detection oil passage 53b or a shutoff position for blocking the travel detection oil passage 53b.

The travel detection oil passage 53b is branched into a signal oil passage 53c on the upstream side of the second travel detection direction switching valve 56f. The signal oil passage 53c is connected to the travel detection pressure sensor 53d. The travel operation levers 413 and 413 are operated, and the first travel detection direction switching valve 56e linked with the first travel direction switching valve 55e or the second travel detection direction switching valve interlocked with the second travel direction switching valve 55f. When the 56f changes from the neutral position to a position other than the neutral position, the travel detection oil passage 53b is blocked and a pressure is applied downstream of the throttle 53e, and this pressure is applied to the travel detection pressure sensor 53d via the signal oil passage 53c. Is entered in. The travel detection pressure sensor 53d converts the input signal pressure into an electric signal and outputs the travel detection signal to the integrated controller 7. As a result, the travel detection pressure sensor 53d can detect that at least one of the first travel motor 22a and the second travel motor 22b is being driven and transmit a travel detection signal.

[Control system configuration]
A negative controller pressure sensor 51k, a travel detection pressure sensor 53d, an electromagnetic proportional valve 51c, and the like are electrically connected to the integrated controller 7.

The integrated controller 7 sends a control command to the electromagnetic proportional valve 51c. The operation of the electromagnetic proportional valve 51c is controlled by the integrated controller 7, and the pilot signal pressure (corresponding to the hydraulic signal) to the pump regulator 51a can be adjusted according to the magnitude of the applied control current value. That is, the control command is, for example, a control current value. The integrated controller 7 generates a control command based on the negative control signal pressure input from the negative control pressure sensor 51k. As a result, the integrated controller 7 can control the discharge amount of the variable displacement pump 51 based on the hydraulic signal according to the negative control pressure. Negative control can also be performed by directly inputting the negative control pressure to the pump regulator 51a.

In the negative control, for example, the larger the lever operation amount of the first work operation lever, that is, the larger the required flow rate of the first work machine actuator 30a, the more the direction switching for the first work machine communicating with the first center bypass oil passage 51d. The bleed-off opening of the valve 55a becomes smaller, the flow rate of the pressure oil passing through the first negative control throttle 51f decreases, and the first negative control pressure becomes lower. When the pressure of the first negative controller becomes low, the discharge amount of the variable displacement pump 51 is increased. As a result, in the negative control, the discharge amount of the variable displacement pump 51 is controlled so as to increase as the lever operation amount increases.

When the travel detection signal transmitted from the travel detection pressure sensor 53d is input, the integrated controller 7 transmits a control command to the electromagnetic proportional valve 51c so as to shut off the hydraulic signal to the pump regulator 51a. By blocking the hydraulic signal to the pump regulator 51a, the discharge amount of the variable displacement pump 51 is maximized.

[Bleed-off opening]
FIG. 3 shows the opening characteristics of the bleed-off opening of the first traveling direction switching valve 55e (or the second traveling direction switching valve 55f) and the direction switching valve 55a for the first working machine (or the direction switching for the second working machine). It is a figure which shows the opening characteristic of the bleed-off opening of a valve 55b). In FIG. 3, 91 shown by a one-point chain line is the opening area characteristic of the bleed-off opening of the directional switching valve 55a for the first working machine, and 92 shown by the solid line is the bleed-off opening of the directional switching valve 55e for the first traveling machine. It is an opening area characteristic. The opening area characteristic of the bleed-off opening of the directional switching valve 55b for the second working machine is the same as that of the directional switching valve 55a for the first working machine, and the opening area of the bleed-off opening of the directional switching valve 55f for the second traveling machine. The characteristics are the same as those of the first traveling direction switching valve 55e.

As shown in FIG. 3, when the directional switching valve 55a for the first working machine is in the neutral position and the lever operating amount of the first working operating lever (working operating lever 412) is zero (direction switching valve for the first working machine). (When the pilot signal pressure applied to 55a is zero), the bleed-off opening communicating with the first center bypass oil passage 51d is fully open, and the opening area is the maximum. As the lever operation amount of the first work operation lever increases, the bleed-off opening closes and the opening area decreases. At this time, the opening area sharply decreases until the lever operating amount reaches L1, the opening area gradually decreases when the lever operating amount exceeds L1, and the bleed-off opening is fully closed when the lever operating amount reaches L2. .. When the lever operation amount of the first work operation lever reaches L1, the first work machine actuator 30a starts driving. The opening area A1 of the bleed-off opening when the lever operating amount of the first work operating lever is L1 is an opening area capable of passing the minimum discharge amount of the variable displacement pump 51. That is, the bleed-off opening of the directional control valve 55a for the first work machine is the variable capacity pump 51 when the operation amount of the first work operation lever reaches a predetermined value L1 and the first work machine actuator 30a starts driving. It has an opening characteristic corresponding to the minimum discharge amount. The bleed-off opening of the directional control valve 55a for the first working machine is an opening area characteristic optimized for negative control, which is an opening area characteristic according to the discharge amount of the variable displacement pump 51 controlled by a hydraulic signal according to the negative control pressure. It can be said that it has.

In the negative control, the opening characteristic of the bleed-off opening of the directional control valve 55 depends on the discharge amount of the variable displacement pump 51 controlled by the negative control pressure of the center bypass oil passage communicating with the bleed-off opening. Therefore, even when the lever operation amount of the first work operation lever is small, the discharge amount of the variable displacement pump 51 is reduced due to the characteristics of the negative control, so that the flow rate of the pressure oil flowing through the first center bypass oil passage 51d is small. As a result, the area of the bleed-off opening in the negative control with respect to the lever operation amount is set smaller than the area of the bleed-off opening in the so-called bleed-off control.

By the way, in the hydraulic circuit 5 having the variable displacement pump 51 controlled by the negative controller, the bleed-off openings of the first traveling direction switching valve 55e and the second traveling direction switching valve 55f are tentatively opened to the first working machine direction switching valve 55a. If the opening area characteristics optimized for negative control are set in the same manner as the bleed-off opening of the directional control valve 55b for the second working machine, the following problems may occur.

For example, when the lever operation amount of the first travel operation lever is large and the lever operation amount of the second travel operation lever is small, that is, the required flow rate of the first travel motor 22a is large and the required flow rate of the second travel motor 22b is large. When it is small, the first negative control pressure becomes lower than the second negative control pressure, the discharge amount of the variable capacity pump 51 is controlled by the first negative control pressure on the low pressure side, and the variable capacity pump 51 runs from the first discharge port P1 to the first run. A large flow rate of pressure oil is discharged according to the required flow rate of the motor 22a. At this time, a large flow rate of pressure oil is discharged from the second discharge port P2 even to the second center bypass oil passage 51e where the required flow rate is small, and the second traveling having an opening area characteristic optimized for negative control control. At the bleed-off opening of the directional control valve 55f, since the opening area is small, the pressure loss is large and abnormal boosting occurs. As a result, the variable displacement pump 51 detects abnormal boosting and reduces the discharge amount by horsepower control in order to prevent engine stall. As a result, the required flow rate of the first traveling motor 22a is not satisfied, and the traveling speed of the first traveling motor 22a drops sharply.

Therefore, in the present invention, the bleed-off openings of the first traveling direction switching valve 55e and the second traveling direction switching valve 55f are openings corresponding to the required flow rates of the pressure oils of the first traveling motor 22a and the second traveling motor 22b. It is configured to have an opening area characteristic optimized for bleed-off control, which is an area characteristic.

Specifically, as shown in FIG. 3, when the first traveling direction switching valve 55e is in the neutral position and the lever operating amount of the first traveling operating lever (traveling operating lever 413) is zero (for the first traveling). (When the pilot signal pressure applied to the directional control valve 55e is zero), the bleed-off opening communicating with the first center bypass oil passage 51d is fully open, and the opening area is the maximum. As the lever operation amount of the first traveling operation lever increases, the bleed-off opening closes and the opening area decreases. At this time, the opening area sharply decreases until the lever operating amount reaches L1, the opening area gradually decreases when the lever operating amount exceeds L1, and the bleed-off opening is fully closed when the lever operating amount reaches L2. .. When the lever operation amount of the first travel operation lever reaches L1, the first travel motor 22a starts driving. The opening area A2 of the bleed-off opening when the lever operating amount of the first traveling operation lever is L1 is an opening area capable of passing the maximum discharge amount of the variable displacement pump 51. The opening area A2 is larger than the opening area A1. That is, the bleed-off opening of the first traveling direction switching valve 55e is the maximum discharge of the variable displacement pump 51 when the operating amount of the first traveling operating lever reaches a predetermined value L1 and the first traveling motor 22a starts driving. It has an opening characteristic corresponding to the amount. It can be said that the bleed-off opening of the first traveling direction switching valve 55e has an opening area characteristic optimized for bleed-off control, which is an opening area characteristic according to the required flow rate of the pressure oil of the first traveling motor 22a.

As described above, the hydraulic circuit 5 of the hydraulic excavator 1 according to the present embodiment is discharged from the split flow type variable capacity pump 51 having the first discharge port P1 and the second discharge port P2 and the variable capacity pump 51. The first traveling motor 22a, the second traveling motor 22b, the first working machine actuator 30a, and the second working machine actuator 30b driven by the pressure oil, and the first center bypass oil passage from the first discharge port P1 to the oil tank. 51d, the second center bypass oil passage 51e from the second discharge port P2 to the oil tank, and the first negative control throttle 51f arranged at the most downstream of the first center bypass oil passage 51d and the second center bypass oil passage 51e, respectively. And a low pressure selection valve 51j that outputs the smaller pressure of the pressure on the upstream side of the first negative control throttle 51f and the second negative control throttle 51g as the negative control pressure, and the hydraulic signal corresponding to the negative control pressure. The integrated controller 7 that controls the discharge amount of the variable displacement pump 51 by
A second traveling direction switching valve 55e arranged in the first center bypass oil passage 51d and controlling the first traveling motor 22a and a second traveling direction switching valve 55e arranged in the second center bypass oil passage 51e and controlling the second traveling motor 22b. The traveling direction switching valve 55f and the first center bypass oil passage 51d are arranged, and the first working machine direction switching valve 55a for controlling the first working machine actuator 30a and the second center bypass oil passage 51e are arranged. A direction switching valve 55b for the second working machine that controls the second working machine actuator 30b, and
A first traveling operation lever for operating the first traveling direction switching valve 55e, a second traveling operating lever for operating the second traveling direction switching valve 55f, and a first working machine direction switching valve 55a. A first work operation lever for operating, a second work operation lever for operating the directional control valve 55b for the second work machine, and
A travel detection pressure sensor 53d that detects that at least one of the first travel motor 22a and the second travel motor 22b is being driven and transmits a travel detection signal is provided.
The bleed-off openings of the first traveling direction switching valve 55e and the second traveling direction switching valve 55f are such that the operating amounts of the first traveling operation lever and the second traveling operation lever reach a predetermined value L1 and the first traveling motor It has an opening characteristic corresponding to the maximum discharge amount of the variable displacement pump 51 when the 22a and the second traveling motor 22b start driving.
The bleed-off openings of the directional switching valve 55a for the first working machine and the directional switching valve 55b for the second working machine have opening characteristics corresponding to the discharge amount of the variable displacement pump 51 controlled based on the negative control pressure.
When the travel detection signal is input, the integrated controller 7 shuts off the hydraulic signal to maximize the discharge amount of the variable displacement pump 51.

According to this configuration, when it is detected that at least one of the first traveling motor 22a and the second traveling motor 22b is being driven, the discharge amount of the variable displacement pump 51 becomes maximum, but the first traveling direction. Since the bleed-off openings of the switching valve 55e and the second traveling directional switching valve 55f have an opening area characteristic optimized for bleed-off control, the first traveling directional switching valve 55e having the smaller lever operation amount of the traveling operation lever Alternatively, an appropriate amount of pressure oil can be bleeded from the bleed-off opening of the second traveling direction switching valve 55f, and the occurrence of abnormal boosting in the first traveling direction switching valve 55e or the second traveling direction switching valve 55f is suppressed. Therefore, it is possible to prevent a sudden decrease in the traveling speed of the traveling motor having a larger lever operating amount of the traveling operation lever. As a result, smooth running performance can be ensured.

Further, in the hydraulic circuit 5 of the hydraulic excavator 1 according to the present embodiment, the area of the bleed-off opening of the first traveling direction switching valve and the second traveling direction switching valve is the area of the first traveling direction switching valve and the first traveling direction switching valve. It is said that the opening characteristic of the bleed-off opening of the second traveling direction switching valve is larger than the area of the bleed-off opening when the opening characteristic corresponds to the discharge amount of the variable displacement pump controlled based on the negative control pressure. It may be configured.

The opening area of the bleed-off opening of the first traveling directional switching valve 55e and the second traveling directional switching valve 55f is the opening characteristic of the bleed-off opening of the first traveling directional switching valve 55e and the second traveling directional switching valve 55f. By setting the opening characteristic to correspond to the discharge amount of the variable capacity pump 51 controlled based on the negative control pressure, the split flow type variable capacity pump 51 controlled by the negative control is set larger than the area of the bleed-off opening. Even if the hydraulic excavator 1 has a gentle turn or a spin turn, an appropriate amount is applied from the bleed-off opening of the first traveling direction switching valve 55e or the second traveling direction switching valve 55f, which has the smaller lever operation amount of the traveling operation lever. The pressure oil can be bleeded, the occurrence of abnormal pressure increase in the first traveling direction switching valve 55e or the second traveling direction switching valve 55f is suppressed, and the traveling motor having the larger lever operation amount of the traveling operation lever It is possible to prevent a sudden decrease in running speed. As a result, smooth running performance can be ensured.

Further, in the hydraulic circuit 5 of the hydraulic excavator 1 according to the present embodiment, the bleed-off openings of the directional switching valve 55a for the first working machine and the directional switching valve 55b for the second working machine are described in the first work operation lever and the first work operation lever. 2 The configuration has an opening characteristic corresponding to the minimum discharge amount of the variable displacement pump 51 when the operation amount of the work operation lever reaches a predetermined value and the first work machine actuator 30a and the second work machine actuator 30b start driving. It may be.

Although the embodiments of the present invention have been described above with reference to the drawings, it should be considered that the specific configuration is not limited to these embodiments. The scope of the present invention is shown not only by the description of the above-described embodiment but also by the scope of claims, and further includes all modifications within the meaning and scope equivalent to the scope of claims.

It is possible to adopt the structure adopted in each of the above embodiments in any other embodiment. The specific configuration of each part is not limited to the above-described embodiment, and various modifications can be made without departing from the gist of the present disclosure.

[Other Embodiments]
In the above embodiment, an example in which the travel detection oil passage 53b, the travel detection pressure sensor 53d, or the like is used as the travel detection means is shown, but the present invention is not limited thereto. As the travel detection means, the first travel is performed by measuring the pilot secondary pressure to be depressurized by the remote control valves of the first travel operation lever and the second travel operation lever that operate the first travel motor 22a and the second travel motor 22b. It may be detected that the motor 22a and the second traveling motor 22b have been operated. Further, as the traveling detection means, a method of measuring and detecting the pressure of the first traveling motor 22a and the second traveling motor 22b with a pressure sensor or the like may be used.

In the above embodiment, an example in which the low pressure selection valve 51j is used as an output means for outputting the smaller of the first negative control pressure and the second negative control pressure as the negative control pressure is shown, but the present invention is not limited to this. The pressure sensor detects and outputs the first negative control pressure and the second negative control pressure, respectively, and the integrated controller 7 selects and outputs the low pressure of the first negative control pressure and the second negative control pressure input from the pressure sensor. You may try to do so.

1: Hydraulic excavator 5: Hydraulic circuit 7: Integrated controller 51: Variable capacity pump 51d: 1st center bypass oil passage 51e: 2nd center bypass oil passage 51f: 1st negative control throttle 51g: 2nd negative control throttle 51j: Low pressure selection valve 51k: Negative control pressure sensor 55: Direction switching valve 55a: Direction switching valve for first working machine 55b: Direction switching valve for second working machine 55e: Direction switching valve for first running 55f: Direction switching valve for second running P1: 1st discharge port P2: 2nd discharge port

Claims (3)

A split-flow type variable capacity pump having a first discharge port and a second discharge port, and a first traveling motor, a second traveling motor, and a first working machine actuator driven by pressure oil discharged from the variable capacity pump. And the second working machine actuator, the first center bypass oil passage from the first discharge port to the oil tank, the second center bypass oil passage from the second discharge port to the oil tank, and the first center bypass oil. The smaller pressure of the first negative control throttle and the second negative control throttle arranged at the most downstream of the path and the second center bypass oil passage, and the pressure on the upstream side of the first negative control throttle and the second negative control throttle, respectively. An output means that outputs as a negative control pressure, a control device that controls the discharge amount of the variable capacitance pump by a hydraulic signal corresponding to the negative control pressure, and a control device.
A first traveling direction switching valve arranged in the first center bypass oil passage and controlling the first traveling motor, and a second traveling vehicle arranged in the second center bypass oil passage and controlling the second traveling motor. The directional control valve, the directional control valve for the first working machine arranged in the first center bypass oil passage and controlling the first working machine actuator, and the second center bypass oil passage arranged in the second center bypass oil passage. A directional control valve for the second work machine that controls the work machine actuator,
The first traveling operation lever for operating the first traveling direction switching valve, the second traveling operating lever for operating the second traveling direction switching valve, and the first working machine direction switching valve are provided. A first work operation lever for operating, a second work operation lever for operating the directional control valve for the second work machine, and the like.
A travel detection means for detecting that at least one of the first travel motor and the second travel motor is being driven and transmitting a travel detection signal is provided.
The bleed-off openings of the first traveling direction switching valve and the second traveling direction switching valve are such that the operating amounts of the first traveling operating lever and the second traveling operating lever reach predetermined values and the first traveling motor And has an opening characteristic corresponding to the maximum discharge amount of the variable displacement pump when the second traveling motor starts driving.
The bleed-off openings of the directional switching valve for the first working machine and the directional switching valve for the second working machine have opening characteristics corresponding to the discharge amount of the variable displacement pump controlled based on the negative control pressure.
The control device is a hydraulic circuit of a construction machine that shuts off the hydraulic signal when the travel detection signal is input and maximizes the discharge amount of the variable displacement pump. The area of the bleed-off opening of the first traveling directional switching valve and the second traveling directional switching valve determines the opening characteristics of the bleed-off opening of the first traveling directional switching valve and the second traveling directional switching valve. The hydraulic circuit of a construction machine according to claim 1, which is larger than the area of the bleed-off opening when the opening characteristic corresponds to the discharge amount of the variable capacity pump controlled based on the negative control pressure. The bleed-off openings of the directional switching valve for the first working machine and the directional switching valve for the second working machine are such that the operating amounts of the first working operation lever and the second working operating lever reach predetermined values and the first The hydraulic circuit of a construction machine according to claim 1 or 2, which has an opening characteristic corresponding to a minimum discharge amount of the variable displacement pump when the working machine actuator and the second working machine actuator start driving.

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