JP7030672B2 - Work machine hydraulic system - Google Patents

Description

The present invention relates to a hydraulic system for working machines such as skid steer loaders and compact truck loaders.

Conventionally, Patent Document 1 is known as a hydraulic system for a working machine. The working machine of Patent Document 1 includes a boom, a bucket, a boom cylinder that operates the boom, a bucket cylinder that operates the bucket, a spare actuator that operates a spare attachment, and a first control valve that controls expansion and contraction of the boom cylinder. A second control valve that controls expansion and contraction of the bucket cylinder and a third control valve that operates a spare actuator are provided.

Japanese Unexamined Patent Publication No. 2010-270527

In the working machine of Patent Document 1, when the spool of the first control valve is not operated, the hydraulic oil discharged from the pump passes through the inside of the first control valve to pass through the inside of the first control valve and the second control valve and the third control valve. It is possible to supply to. On the other hand, when the spool of the first control valve is operated, the hydraulic oil (return oil) returned from the boom cylinder to the first control valve can be supplied to the second control valve and the third control valve. .. That is, in the hydraulic circuit of the working machine of Patent Document 1, the return oil returned from the upstream control valve (first control valve) is supplied to the downstream control valve (second control valve, third control valve). The series circuit is adopted. However, in the series circuit, it may be difficult to operate the second control valve, the third control valve, etc. on the downstream side when the control valve on the upstream side is operated.

The present invention has been made to solve the problems of the prior art as described above, and is a hydraulic system for a working machine capable of easily operating a plurality of control valves (hydraulic actuators) in a series circuit. The purpose is to provide.

The technical means of the present invention for solving this technical problem is as follows.
The hydraulic system of the working machine of the present invention controls a hydraulic pump for discharging hydraulic oil, a first hydraulic actuator, a second hydraulic actuator, and the first hydraulic actuator when the switching position is switched to a predetermined switching position. The first control valve, the second control valve provided on the downstream side of the first control valve and controlling the second hydraulic actuator, and the first control valve and the first hydraulic actuator are connected to each other and the first hydraulic actuator is connected. 1 A return oil passage through which the return oil discharged from the hydraulic actuator flows, a first internal oil passage provided in the first control valve and communicating with the return oil passage, and the first internal oil passage communicating with the first internal oil passage. An external oil passage connecting the first control valve and the second control valve, a discharge oil passage connected to a discharge portion where the hydraulic oil is discharged, and a branch from the external oil passage to the discharge oil passage. A connected branch oil passage, a pressure rising portion provided in the discharge oil passage and increasing the pressure of the discharge oil passage, and a first control valve provided in the first control valve and the first control valve at a predetermined switching position. It is provided with a second internal oil passage that communicates with the external oil passage when switched and returns the hydraulic oil flowing through the external oil passage to the first control valve.

The first control valve has an input port and an output port, and has a neutral position in which hydraulic oil different from the return oil is passed through the first control valve and flows to the second control valve. It is possible to switch to a side position where the return oil of the first internal oil passage flows into the external oil passage and the hydraulic oil of the second internal oil passage is returned to the input port at a predetermined switching position.
The hydraulic system of the work machine includes a boom, the first hydraulic actuator is a boom cylinder for operating the boom, and the side position is an ascending position for operating the boom cylinder to raise the boom. It includes a lowering position for operating the boom cylinder to lower the boom.

When the first control valve is in the descending position, the return oil is passed through the first internal oil passage and the external oil passage, and the hydraulic oil in the discharge oil passage is passed through the branch oil passage to the outside. It is passed through the oil passage and the second inner oil passage.
The hydraulic system of the work machine includes a bucket, the first hydraulic actuator is a bucket cylinder for operating the bucket, and the first control valve is a scooping position for operating the bucket cylinder to scoop the bucket. And a dump position for operating the bucket cylinder in order to dump the bucket.

When the first control valve is in the scooping position, the return oil is passed through the first internal oil passage and the external oil passage, and the hydraulic oil in the discharge oil passage is passed through the branch oil passage. It is passed through the outer oil passage and the second inner oil passage.

According to the present invention, a plurality of control valves (hydraulic actuators) can be easily operated in a series circuit.

It is a figure which shows the hydraulic system (hydraulic circuit) in 1st Embodiment. It is a figure which shows the hydraulic system (hydraulic circuit) in 2nd Embodiment. It is a figure which shows the 1st modification example of a check valve and a return discharge oil passage. It is a figure which shows the 2nd modification of the check valve and the return oil passage. It is an overall view of the skid steer loader exemplified as a working machine.

Hereinafter, a hydraulic system for a working machine according to the present invention and a preferred embodiment of the working machine provided with the hydraulic system will be described with reference to the drawings as appropriate.
[First Embodiment]
First, the working machine will be described.
FIG. 4 shows a side view of the working machine according to the present invention. FIG. 4 shows a skid steer loader as an example of a working machine. However, the working machine according to the present invention is not limited to the skid sterode, and may be, for example, another type of loader working machine such as a compact truck loader. Further, it may be a working machine other than the loader working machine.

The working machine 1 includes a machine body (body) 2, a cabin 3, a working device 4, and traveling devices 5A and 5B.
A cabin 3 is mounted on the aircraft 2. A driver's seat 8 is provided at the rear of the cabin 3. In the embodiment of the present invention, the front side (left side of FIG. 4) of the driver seated in the driver's seat 8 of the work machine 1 is the front, the rear side of the driver (right side of FIG. 4) is the rear, and the left side of the driver (FIG. 4). The front side of No. 4) will be described as the left side, and the right side of the driver (the back side of FIG. 4) will be described as the right side. Further, the horizontal direction, which is a direction orthogonal to the front-rear direction, will be described as the body width direction. The direction from the center of the machine 2 to the right or left side will be described as the outside of the machine. In other words, the outside of the airframe is the width direction of the airframe and the direction away from the airframe 2. The direction opposite to the outside of the aircraft will be described as the inside of the aircraft. In other words, the inside of the machine is the width direction of the machine and the direction approaching the body 2.

The cabin 3 is mounted on the airframe 2. The work device 4 is a device for performing work and is equipped on the machine body 2. The traveling device 5A is a device for traveling the machine body 2, and is provided on the left side side of the machine body 2. The traveling device 5B is a device for traveling the machine body 2, and is provided on the right side of the machine body 2. A motor 7 is provided at the rear part of the machine 2. The prime mover 7 is a diesel engine (engine). The prime mover 7 is not limited to the engine, but may be an electric motor or the like.

A traveling lever 9L is provided on the left side of the driver's seat 8. A traveling lever 9R is provided on the right side of the driver's seat 8. The traveling lever 9L on the left side operates the traveling device 5A on the left side, and the traveling lever 9R on the right side operates the traveling device 5B on the right side.
The working device 4 has a boom 10, a bucket 11, a lift link 12, a control link 13, a boom cylinder 14, and a bucket cylinder 17. The boom 10 is provided on the side of the machine body 2. The bucket 11 is provided at the tip (front end) of the boom 10. The lift link 12 and the control link 13 support the base (rear part) of the boom 10. The boom cylinder 14 drives the boom 10 up or down.
Specifically, the lift link 12, the control link 13, and the boom cylinder 14 are provided on the side of the machine body 2. The upper part of the lift link 12 is pivotally supported on the upper part of the base of the boom 10. The lower part of the lift link 12 is pivotally supported on the rear side of the machine body 2. The control link 13 is arranged in front of the lift link 12. One end of the control link 13 is pivotally supported by the lower part of the base of the boom 10, and the other end is pivotally supported by the machine body 2.

The boom cylinder 14 is a hydraulic cylinder that raises and lowers the boom 10. The upper portion of the boom cylinder 14 is pivotally supported by the front portion of the base of the boom 10. The lower portion of the boom cylinder 14 is pivotally supported on the side portion of the rear portion of the machine body 2. When the boom cylinder 14 is expanded and contracted, the boom 10 swings up and down by the lift link 12 and the control link 13. The bucket cylinder 17 is a hydraulic cylinder that swings the bucket 11. The bucket cylinder 17 connects between the left portion of the bucket 11 and the left boom, and also connects between the right portion and the right boom of the bucket 11. A spare attachment such as a hydraulic crusher, a hydraulic breaker, an angle bloom, an auger, a pallet fork, a sweeper, a mower, or a snow blower can be attached to the tip (front portion) of the boom 10 instead of the bucket 11. ..

As the traveling devices 5A and 5B, wheel-type traveling devices 5A and 5B having front wheels 5F and rear wheels 5R are adopted in the present embodiment. As the traveling devices 5A and 5B, crawler type (including semi-crawler type) traveling devices 5A and 5B may be adopted.
Next, the work system hydraulic circuit (work system hydraulic system) provided in the skid steer loader 1 will be described.

The working hydraulic system is a system that operates a boom 10, a bucket 11, a spare attachment, etc., and as shown in FIG. 1, a plurality of control valves 20 and a working hydraulic pump (first hydraulic pump) P1 are used. I have. Further, a second hydraulic pump P2 different from the first hydraulic pump P1 is provided.
The first hydraulic pump P1 is a pump operated by the power of the prime mover 7, and is composed of a constant capacity type gear pump. The first hydraulic pump P1 can discharge the hydraulic oil stored in the tank (hydraulic oil tank) 15. The second hydraulic pump P2 is a pump operated by the power of the prime mover 7, and is composed of a constant capacity type gear pump. The second hydraulic pump P2 can discharge the hydraulic oil stored in the tank (hydraulic oil tank) 15. The second hydraulic pump P2 discharges hydraulic oil for signals and hydraulic oil for control in the hydraulic system. The hydraulic oil for signals and the hydraulic oil for control are called pilot oils.

The plurality of control valves 20 are valves for controlling various hydraulic actuators provided in the working machine 1. A hydraulic actuator is a device operated by hydraulic oil, such as a hydraulic cylinder and a hydraulic motor. In this embodiment, the plurality of control valves 20 are a boom control valve 20A, a bucket control valve 20B, and a preliminary control valve 20C.
The boom control valve 20A is a valve that controls the hydraulic actuator (boom cylinder) 14 that operates the boom 10. The boom control valve 20A is a linear motion spool type 3-position switching valve. The boom control valve 20A switches to the neutral position 20a3, the first position 20a1 different from the neutral position 20a3, the neutral position 20a3, and the second position 20a2 different from the first position 20a1. The first position 20a1 and the second position 20a2 are side positions.

In the boom control valve 20A, the neutral position 20a3, the first position 20a1, and the second position 20a2 are switched by moving the spool by operating the operating member. The boom control valve 20A is switched by directly moving the spool by manually operating the operating member, but the spool is moved by hydraulic operation (hydraulic operation by the pilot valve, hydraulic operation by the proportional valve). It may be moved by an electric operation (electric operation by exciting a solenoid), or may be moved by another method.

The boom control valve 20A and the first hydraulic pump P1 are connected by a discharge oil passage 27. Further, the boom control valve 20A and the boom cylinder 14 are connected by an oil passage 21.
Specifically, the boom cylinder 14 includes a cylinder body 14a, a rod 14b movably provided on the cylinder body 14a, and a piston 14c provided on the rod 14b. A first port 14d for supplying and discharging hydraulic oil is provided at the base end portion (the side opposite to the rod 14b side) of the tubular body 14a. A second port 14e for supplying and discharging hydraulic oil is provided at the tip of the cylinder 14a (on the rod 14b side).

The oil passage 21 includes a first connecting oil passage 21a that connects the first port 31 of the boom control valve 20A and the first port 14d of the boom cylinder 14, and the second port 32 of the boom control valve 20A and the first port of the boom cylinder 14. It has a second connecting oil passage 21b that connects the two ports 14e.
Therefore, if the boom control valve 20A is set to the first position (rising position) 20a1 which is the side position, hydraulic oil can be supplied from the first connecting oil passage 21a to the first port 14d of the boom cylinder 14. Hydraulic oil can be discharged from the second port 14e of the boom cylinder 14 to the second connecting oil passage 21b. As a result, the boom cylinder 14 is extended and the boom 10 is raised. If the boom control valve 20A is set to the second position (lowering position) 20a2, which is the side position, hydraulic oil can be supplied from the second connecting oil passage 21b to the second port 14e of the boom cylinder 14, and the boom cylinder. Hydraulic oil can be discharged from the first port 14d of 14 to the first connecting oil passage 21a. As a result, the boom cylinder 14 contracts and the boom 10 descends.

The bucket control valve 20B is a valve that controls a hydraulic cylinder (bucket cylinder) 17 that controls the bucket 11. The bucket control valve 20B is a pilot type direct-acting spool type 3-position switching valve. The bucket control valve 20B switches to the neutral position 20b3, the first position 20b1 different from the neutral position 20b3, the neutral position 20b3, and the second position 20b2 different from the first position 20b1. The second position 20b2, which is different from the first position 20b1, is a side position.

In the bucket control valve 20B, the neutral position 20b3, the first position 20b1 and the second position 20b2 are switched by moving the spool by operating the operating member. The bucket control valve 20B is switched by directly moving the spool by manually operating the operating member, but the spool is moved by hydraulic operation (hydraulic operation by the pilot valve, hydraulic operation by the proportional valve). It may be moved by an electric operation (electric operation by exciting a solenoid), or may be moved by another method.

The bucket control valve 20B and the bucket cylinder 17 are connected by an oil passage 22. Specifically, the bucket cylinder 17 includes a cylinder 17a, a rod 17b movably provided on the cylinder 17a, and a piston 17c provided on the rod 17b. A first port 17d for supplying and discharging hydraulic oil is provided at the base end portion (the side opposite to the rod 17b side) of the tubular body 17a. A second port 17e for supplying and discharging hydraulic oil is provided at the tip of the cylinder 17a (on the rod 17b side).

The oil passage 22 includes a first connecting oil passage 22a connecting the first port 35 of the bucket control valve 20B and the second port 17e of the bucket cylinder 17, and the second port 36 of the bucket control valve 20B and the bucket cylinder 17. It has a second connecting oil passage 22b that connects to one port 17d.
Therefore, if the bucket control valve 20B is set to the first position (scooping position) 20b1 which is the side position, hydraulic oil can be supplied from the first connecting oil passage 22a to the second port 17e of the bucket cylinder 17. Hydraulic oil can be discharged from the first port 17d of the bucket cylinder 17 to the second connecting oil passage 22b. As a result, the bucket cylinder 17 contracts and the bucket 11 squeezes. If the bucket control valve 20B is set to the second position (dump position) 20b2, which is the side position, hydraulic oil can be supplied from the second connecting oil passage 22b to the first port 17d of the bucket cylinder 17, and the bucket can be supplied. Hydraulic oil can be discharged from the second port 17e of the cylinder 17 to the first connecting oil passage 22a. As a result, the bucket cylinder 17 expands and dumps.

The spare control valve 20C is a valve that controls a hydraulic actuator (hydraulic cylinder, hydraulic motor, etc.) 16 mounted on the spare attachment. The preliminary control valve 20C is a pilot type direct-acting spool type 3-position switching valve. The preliminary control valve 20C switches to the neutral position 20c3, the first position 20c1 different from the neutral position 20c3, the neutral position 20c3, and the second position 20c2 different from the first position 20c1. In the preliminary control valve 20C, the neutral position 20c3, the first position 20c1 and the second position 20c2 are switched by moving the spool by the pressure of the pilot oil. A connecting member 18 is connected to the preliminary control valve 20C via oil supply / drainage passages 83a and 83b. An oil passage connected to the hydraulic actuator (preliminary hydraulic actuator) 16 of the spare attachment is connected to the connecting member 18.

Therefore, if the spare control valve 20C is set to the first position 20c1, hydraulic oil can be supplied from the oil supply / drainage passage 83a to the hydraulic actuator 16 of the spare attachment. If the spare control valve 20C is set to the second position 20c2, hydraulic oil can be supplied from the oil supply / drainage passage 83b to the hydraulic actuator 16 of the spare attachment. In this way, the hydraulic actuator 16 (spare attachment) can be operated by supplying hydraulic oil to the hydraulic actuator 16 from the oil supply / drainage passage 83a or the oil supply / drainage passage 83b.

By the way, in the hydraulic system, a series circuit (series oil passage) is applied. In the series circuit, the hydraulic oil returned from the hydraulic actuator to the control valve on the upstream side can be supplied to the control valve on the downstream side. For example, focusing on the boom control valve 20A and the bucket control valve 20B, the boom control valve 20A is the control valve on the upstream side, and the bucket control valve 20B is the control valve on the downstream side.

Hereinafter, the control valve on the upstream side is referred to as a "first control valve", and the control valve on the downstream side is referred to as a "second control valve". Further, the hydraulic actuator corresponding to the first control valve is referred to as a "first hydraulic actuator", and the hydraulic actuator corresponding to the second control valve is referred to as a "second hydraulic actuator". The oil passage that supplies the return oil, which is the hydraulic oil that returns from the first hydraulic actuator to the first control valve, to the second control valve is referred to as a "first oil passage".

In this embodiment, the boom control valve 20A is a "first control valve" and the bucket control valve 20B is a "second control valve". Further, the boom cylinder 14 is a "first hydraulic actuator" and the bucket cylinder 17 is a "second hydraulic actuator".
Hereinafter, the first control valve and the second control valve will be described in detail.
The first control valve 20A and the discharge portion of the first hydraulic pump P1 are connected by a discharge oil passage 27. The discharge oil passage 27 branches at the middle portion 47a and reaches the first control valve 20A. The oil passage after the branch of the discharge oil passage 27 is connected to the first input port 46a and the second input port 46b of the first control valve 20A. Further, the discharge oil passage 27 is connected to the third input port 46c of the first control valve 20A. Therefore, the hydraulic oil discharged from the first hydraulic pump P1 can be supplied into the first control valve 20A through the discharge oil passage 27, the first input port 46a, the second input port 46b, and the third input port 46c. Is. In the discharge oil passage 27, a discharge oil passage 24 capable of discharging hydraulic oil is connected to a section between the intermediate portion 47a and the third input port 46c. The discharge oil passage 24a is provided with a relief valve (main relief valve) 25 capable of discharging hydraulic oil when the pressure of the discharge oil passage 27 becomes a predetermined pressure or more (set pressure or more). The second discharge oil passage 24b connected to the first discharge oil passage 24a and reaching the discharge portion for discharging the hydraulic oil, and the first discharge port 33a of the first control valve 20A connected to the second discharge oil passage 24b. It includes a third discharge oil passage 24c leading to the second discharge port 33b. The discharge portion is a hydraulic oil tank and a suction portion (a portion for sucking hydraulic oil) of the hydraulic pump. Further, the discharge portion may be any portion as long as it is a portion where the hydraulic oil is discharged, and may be other than the suction portion of the hydraulic oil tank and the hydraulic pump.

The pressure rising portion 130 is provided in the second drainage channel 24b. The pressure rising portion 130 is a portion that raises the pressure of the drainage oil passage 24. Further, the pressure increasing portion 130 is provided in the fourth discharge oil passage 24 in parallel with the second discharge oil passage 24b in the discharge oil passage 24. The pressure rising portion 130 is an oil cooler, a relief valve, a throttle portion (throttle valve), a choke valve, a check valve, or the like. Further, a plurality of pressure rising portions 130 may be provided in the second drainage passage 24b, and the connection method may be in series or in parallel. Further, although two discharge oil passages 24 are provided from the control valve on the most downstream side, the number of the discharge oil passages 24 may be one, and when there is one discharge oil passage 24, the pressure riser portion. There may be one 130.

The first control valve 20A and the second control valve 20B are connected by a central oil passage 51. The central oil passage 51 connects the third output port 41c of the first control valve 20A and the third input port 42c of the second control valve 20B.
The first control valve 20A and the second control valve 20B are connected to each other by a first oil passage 61 in addition to the central oil passage 51. The first oil passage 61 is an oil passage for supplying the return oil returning from the first hydraulic actuator 14 to the first control valve 20A to the second control valve 20B through the first control valve 20A.

The first oil passage 61 has a first connecting oil passage (first return oil passage) 21a, a first internal oil passage 61a, and an external oil passage 61b. The first connecting oil passage 21a is an oil passage connecting the first port 31 of the first control valve 20A and the first port 14d of the first hydraulic actuator 14, and is the first port 14d of the first hydraulic actuator 14. This is the first return oil passage through which the return oil discharged from the oil flow flows.

The first internal oil passage 61a is an oil passage provided in the first control valve 20A and communicating with the first return oil passage 21a. Specifically, the first internal oil passage 61a connects the first port 31 of the first control valve 20A and the first output port 41a of the first control valve 20A when the first control valve 20A is set to the second position 20a2. It is an oil channel to connect.
The external oil passage 61b is an oil passage that communicates with the first internal oil passage 61a and connects to the second control valve 20B. The external oil passage 61b connects the first output port 41a of the first control valve 20A and the first input port 42a of the second control valve 20B, and the second output port 41b and the second of the first control valve 20A. It is connected to the second input port 42b of the control valve 20B. The middle part of the external oil passage 61b is connected to the central oil passage 53c.

Further, in the working hydraulic system, a second internal oil passage 150 is provided separately from the first internal oil passage 61a. The second internal oil passage 150 is an oil passage that communicates with the external oil passage 61b when the first control valve 20A is switched to a predetermined switching position. Specifically, the second internal oil passage 150 has a third output port 41c of the first control valve 20A and a third input port 46c of the first control valve 20A when the first control valve 20A is set to the second position 20a2. It is an oil channel that connects.

Further, the working hydraulic system includes a branch oil passage 100. The branch oil passage 100 is an oil passage provided on the downstream side of the spool of the first control valve 20A, and the return oil that branches from the external oil passage 61b and passes through the external oil passage 61b passes through or is discharged. The hydraulic oil in the oil passage 24 passes through. One end of the branch oil passage 100 is connected to the external oil passage 61b, and the other end is connected to the third discharge oil passage 24c.

A throttle portion 101 is connected to the branch oil passage 100. The throttle portion 101 is configured, for example, by making a part of the branch oil passage 100 thinner than the other parts. In other words, the throttle portion 101 is configured by making the cross-sectional area of the portion where the hydraulic oil flows in the branch oil passage 100 smaller than that of the other portions. The configuration of the branch oil passage 100 is not limited to the above-mentioned example.

A check valve 102 is connected to the external oil passage 61b. The check valve 102 is a valve that allows the return oil to flow from the first control valve 20A to the second control valve 20B and prevents the hydraulic oil from flowing from the second control valve 20B to the branch oil passage 100. .. Specifically, the check valve 102 is a first connecting portion 110 in which the external oil passage 61b and the branch oil passage 100 are connected, and the external oil passage 61b and the second control valve 20B are connected to each other in the external oil passage 61b. It is provided in a section with two connection portions (first input port 42a, second input port 42b).

According to the above, when the first control valve 20A is set to the second position (lowering position) 20a2, the first connecting oil passage (first return oil passage) 21a, the first internal oil passage 61a and the external oil passage 61b are connected. Will be done. Therefore, as shown by the arrow A1 in FIG. 1, the return oil returned from the first hydraulic actuator 14 to the first control valve 20A passes through the first return oil passage 21a and the first internal oil passage 61a, and is external oil. It flows toward the road 61b. Further, as shown by arrow A2, the hydraulic oil flowing from the first internal oil passage 61a to the external oil passage 61b is the check valve 102 and the connection portion 66 (central oil passage 51 and external oil passage 61b) of the external oil passage 61b. The second control valve 20B is reached through the connecting portion).

Here, the hydraulic oil supplied from the first control valve 20A to the first hydraulic actuator 14 is low, that is, the hydraulic oil supplied from the discharge oil passage 27 to the second input port 46b of the first control valve 20A ( It is assumed that the supply oil) is low (hydraulic oil shortage situation). In the hydraulic oil shortage situation, as shown by arrows A3 and A4 in FIG. 1, the hydraulic oil discharged from the downstream side of the first control valve 20A to the discharge oil passage 24 flows into the second discharge oil passage 24b and the third It flows into the discharge oil passage 24c and flows from the branch oil passage 100 to the external oil passage 61b.

That is, since the pressure rising portion 130 is provided in the second discharge oil passage 24b, at least a part of the hydraulic oil flowing through the second discharge oil passage 24b is the third discharge oil passage 24c and the branch oil passage 100. Will return to the external oil passage 61b via.
Further, when the first control valve 20A is set to the second position (lowering position) 20a2, the third output port 41c of the first control valve 20A and the third input of the first control valve 20A are provided by the second internal oil passage 150. Since it communicates with the port 46c, as shown by the arrow A5 in FIG. 1, the hydraulic oil that has returned to the external oil passage 61b via the third discharge oil passage 24c and the branch oil passage 100 connects the connecting portion 66. After passing through, it enters the first control valve 20A from the third output port 41c, passes through the second internal oil passage 150, and returns to the discharge oil passage 27 from the third input port 46c. As shown by the arrow A6 in FIG. 1, the hydraulic oil returned to the discharge oil passage 27 passes through the intermediate portion 47a, heads for the first control valve 20A, and is supplied to the first control valve 20A from the second input port 46b. Ru. The hydraulic oil supplied to the first control valve 20A is supplied to the first hydraulic actuator 14 from the second port 32 of the first control valve 20A through the second connecting oil passage 21b.

As described above, since the second internal oil passage 150, the pressure rising portion 130, and the branch oil passage 100 are provided, if the supply oil supplied to the first hydraulic actuator 14 is insufficient, the drain oil passage is provided. Twenty-four hydraulic oils can be replenished.
[Second Embodiment]
FIG. 2 shows the hydraulic system (hydraulic circuit) of the working machine in the second embodiment. The same parts as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. In the second embodiment, for convenience of explanation, the bucket control valve 20B is referred to as a “first control valve” and the preliminary control valve 20C is referred to as a “second control valve”. Further, the bucket cylinder 17 is referred to as a "first hydraulic actuator", and the hydraulic actuator 16 is referred to as a "second hydraulic actuator".

The first control valve 20B and the second control valve 20C are connected by a central oil passage 72. The central oil passage 72 connects the third output port 43c of the first control valve 20B and the third input port 44c of the second control valve 20C.
The first control valve 20B and the second control valve 20C are connected to each other by a first oil passage 81 in addition to the central oil passage 72. The first oil passage 81 is an oil passage for supplying the return oil returning from the first hydraulic actuator 17 to the first control valve 20B to the second control valve 20C through the first control valve 20B.

The first oil passage 81 has a second connecting oil passage (first return oil passage) 22b, a first internal oil passage 81a, and an external oil passage 81b. The second connecting oil passage 22b is an oil passage connecting the second port 36 of the first control valve 20B and the first port 17d of the first hydraulic actuator 17, and the return oil discharged from the first port 17d. This is the first return oil passage through which
The first internal oil passage 81a is an oil passage provided in the first control valve 20B and communicating with the second return oil passage 22b. Specifically, the first internal oil passage 81a has a second port 36 of the first control valve 20B and a second output port 43b of the first control valve 20B when the first control valve 20B is set to the first position 20b1. It is an oil channel to connect.

The external oil passage 81b is an oil passage that communicates with the first internal oil passage 81a and connects to the second control valve 20C. The external oil passage 81b connects the first output port 43a of the first control valve 20B and the first input port 44a of the second control valve 20C, and the second output port 43b and the second of the first control valve 20B. It is connected to the second input port 44b of the control valve 20C. The middle part of the outer oil passage 81b is connected to the central oil passage 73c.

Also in the second embodiment, it is possible to discharge the return oil passing through the external oil passage 81b and return the hydraulic oil in the discharge oil passage 24 to the external oil passage 81b. The working hydraulic system includes a branch oil passage 200. The branch oil passage 200 is an oil passage provided on the downstream side of the spool of the first control valve 20B, and discharges the return oil that branches from the external oil passage 81b and passes through the external oil passage 81b to the discharge unit. .. Specifically, one end of the branch oil passage 200 is connected to the external oil passage 81b, and the other end is connected to the third discharge oil passage 24c.

A throttle portion 201 is connected to the branch oil passage 200. The throttle portion 201 is configured, for example, by making a part of the branch oil passage 200 thinner than the other portion. In other words, the throttle portion 201 is configured by making the cross-sectional area of the portion of the branch oil passage 200 through which the hydraulic oil flows smaller than that of the other portions. The configuration of the branch oil passage 200 is not limited to the above-mentioned example.

A check valve 202 is connected to the external oil passage 81b. The check valve 202 is a valve that allows the return oil to flow from the first control valve 20B to the second control valve 20C and prevents the hydraulic oil from flowing from the second control valve 20C to the branch oil passage 200. .. Specifically, the check valve 202 is a first connecting portion 210 in which the external oil passage 81b and the branch oil passage 200 are connected, and the external oil passage 81b and the second control valve 20C are connected to each other in the external oil passage 81b. It is provided in a section with two connection portions (first input port 44a, second input port 44b).

In the second control valve 20C, the second internal oil passage 250 is an oil passage that communicates with the external oil passage 81b when the first control valve 20B is switched to a predetermined switching position. Specifically, the second internal oil passage 250 has a third output port 43c of the first control valve 20B and a third input port 42c of the first control valve 20B when the first control valve 20B is set to the first position 20b1. It is an oil channel that connects.

According to the above, when the first control valve 20B is set to the second position (scooping position) 20b1, the first connecting oil passage (first return oil passage) 22b, the first internal oil passage 81a and the external oil passage 81b are connected. Will be done. Therefore, the return oil returned from the first hydraulic actuator 14 to the first control valve 20B is the first return oil passage 22b, the first internal oil passage 81a, the external oil passage 81b, and the connection portion 67 (central oil passage 72 and external oil). It passes through the connection portion (connecting portion connecting to the road 81b) and reaches the second control valve 20B.

Here, in the hydraulic oil shortage situation in the first control valve 20B, the hydraulic oil discharged from the downstream side of the first control valve 20B to the discharge oil passage 24 flows into the third discharge oil passage 24c and from the branch oil passage 200. It flows into the external oil passage 81b.
Further, the hydraulic oil that has returned to the external oil passage 81b via the third discharge oil passage 24c and the branch oil passage 100 passes through the connecting portion 67, enters the first control valve 20B from the third output port 43c, and enters the first control valve 20B. It passes through the second internal oil passage 250 and returns from the third input port 42c to the oil passage (external oil passage) 61b on the downstream side. The hydraulic oil returned to the oil passage (external oil passage) 61b is supplied to the first control valve 20B from the first input port 44a of the first control valve 20B. The hydraulic oil supplied to the first control valve 20B is supplied to the first hydraulic actuator 14 from the first port 35 of the first control valve 20B through the first connecting oil passage 22a.

As described above, since the second internal oil passage 250, the pressure rising portion 130, and the branch oil passage 200 are provided, if the supply oil supplied to the first hydraulic actuator 14 is insufficient, the drain oil passage is provided. Twenty-four hydraulic oils can be replenished.
The branch oil passages 100, 200, check valves 102, 202, etc. can be changed as shown in FIGS. 3A and 3B.

As shown in FIG. 3A, in the external oil passage 61b, the oil passage connected to the first output port 41a and the oil passage connected to the second output port 41b meet on the upstream side of the confluence 111. A valve 102 may be provided. In this case, in the external oil passage 61b, the branch oil passage 100 is connected to the section from the first output port 41a of the first control valve 20A to the merging portion 111 where the check valve 102 is provided. By doing so, when the boom 10 is lowered (when the boom control valve 20A is set to the second position 20a2), the hydraulic oil in the discharge oil passage 24 (third discharge oil passage 24c) is used in the branch oil passage 100. The external oil passage 61b can be replenished through the oil passage 61b.

As shown in FIG. 3B, in the external oil passage 81b, the oil passage connected to the first output port 43a and the oil passage connected to the second output port 43b meet on the upstream side of the confluence portion 211. A valve 202 may be provided. In this case, in the external oil passage 81b, the return branch oil passage 200 is connected to the section from the first control valve 20B to the merging portion 211 where the check valve 202 is provided. By doing so, when the first hydraulic actuator 17, that is, the bucket 11 is squeezed (when the bucket control valve 20B is set to the first position 20b1), the drainage oil passage 24 (third drainage oil passage 24c) The hydraulic oil of the above can be replenished to the external oil passage 81b via the branch oil passage 200.

It should be noted that the embodiments disclosed this time are exemplary in all respects and are not restrictive. The scope of the present invention is shown by the scope of claims rather than the above description, and is intended to include all modifications within the meaning and scope equivalent to the scope of claims. The first control valve and the second control valve are not limited to the above-described embodiment, and may be any control valve provided in the working machine. In the above-described embodiment, the hydraulic pump is a constant-capacity pump, but for example, it may be a variable-capacity pump whose discharge amount changes by changing the swash plate, or another hydraulic pump.

1: Working machine 14: Boom cylinder 17: Bucket cylinder 20: Control valve 20A: Boom control valve 20B: Bucket control valve 20C: Preliminary control valve 24: Drainage oil passage 24a: First discharge oil passage 24b: Second discharge oil passage 24c: Third discharge oil passage 27: Discharge oil passage 47: Discharge oil passage 47a: Midway portion 61a: First internal oil passage 61b: External oil passage 66: Connection portion 67: Connection portion 81a: First internal oil passage 81b: External oil passage 83a: Supply / drain passage 83b: Supply / drain passage 100: Branch oil passage 101: Squeezing portion 102: Check valve 130: Pressure rise portion 150, 250: Second internal oil passage 200: Branch oil passage 201: Squeezing part 202: Check valve P1: 1st hydraulic pump P2: 2nd hydraulic pump

Claims (6)

A hydraulic pump that discharges hydraulic oil and
With the first hydraulic actuator,
With the second hydraulic actuator,
A first control valve that controls the first hydraulic actuator when switched to a predetermined switching position,
A second control valve provided on the downstream side of the first control valve and controlling the second hydraulic actuator,
A return oil passage that connects the first control valve and the first hydraulic actuator and allows the return oil discharged from the first hydraulic actuator to flow.
A first internal oil passage provided in the first control valve and communicating with the return oil passage, and
An external oil passage that communicates with the first internal oil passage and connects the first control valve and the second control valve.
An oil discharge passage connected to the discharge part where the hydraulic oil is discharged , and
A branch oil passage that branches from the external oil passage and is connected to the discharge oil passage,
A pressure riser provided in the drainage channel and increasing the pressure of the drainage channel,
When the first control valve is provided in the first control valve and the first control valve is switched to a predetermined switching position, the hydraulic oil that communicates with the external oil passage and flows into the external oil passage is used as the first control valve. The second internal oil passage to return and
The hydraulic system of the working machine. The first control valve has an input port and an output port, and has a neutral position in which hydraulic oil different from the return oil is passed through the first control valve and flows to the second control valve. A claim that the return oil of the first internal oil passage can be switched to a side position where the return oil of the first internal oil passage flows into the external oil passage and the hydraulic oil of the second internal oil passage is returned to the input port at a predetermined switching position. Item 1. The hydraulic system of the working machine according to Item 1. With a boom,
The first hydraulic actuator is a boom cylinder that operates the boom.
The hydraulic system according to claim 2, wherein the side position includes an ascending position for operating the boom cylinder to raise the boom and a descending position for operating the boom cylinder to lower the boom. When the first control valve is in the descending position, the return oil is passed through the first internal oil passage and the external oil passage, and the hydraulic oil in the discharge oil passage is passed through the branch oil passage to the outside. The hydraulic system for a working machine according to claim 3, wherein the oil passage is passed through the oil passage and the second internal oil passage. Equipped with a bucket
The first hydraulic actuator is a bucket cylinder that operates the bucket.
The first control valve according to claim 2, wherein the first control valve includes a scooping position for operating the bucket cylinder to scoop the bucket and a dump position for operating the bucket cylinder to dump the bucket. Hydraulic system. When the first control valve is in the scooping position, the return oil is passed through the first internal oil passage and the external oil passage, and the hydraulic oil in the discharge oil passage is passed through the branch oil passage. The hydraulic system for a working machine according to claim 5, which is passed through an external oil passage and the second internal oil passage.

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