HYDRAULIC SYSTEM FOR WORKING MACHINE

CROSS-REFERENCE TO RELATED APPLICATIONS

The present application claims priority under 35 U.S.C. § 119 to Japanese Patent Application No. 2016-255461, filed Dec. 28, 2016 and to Japanese Patent Application No. 2017-227076, filed Nov. 27, 2017. The contents of these applications are incorporated herein by reference in their entirety.

BACKGROUND OF THE INVENTION
Field of the Invention

The present invention relates to a hydraulic system for a working machine such as a skid steer loader, a compact track loader, and the like.

Discussion of the Background

Japanese Patent Publication No. 5809544 previously discloses a technique for warming up a working machine.

The working machine disclosed in Japanese Patent Publication No. 5809544 includes a pilot pressure control valve and a valve body. The pilot pressure control valve is configured to control a pressure of a pilot fluid outputted from a pump and sent to a supplying target. The valve body incorporates the pilot pressure control valve. In the working machine disclosed in Japanese Patent Publication No. 5809544, the valve body is provided with a heat-up fluid tube into which the pilot fluid outputted from the pump is supplied, the pilot fluid supplied into the heat-up fluid tube is supplied to an operation fluid tank through a relief valve or a throttle, and thereby the valve body is heated up.

SUMMARY OF THE INVENTION

A hydraulic system for a working machine of the present invention, includes a hydraulic pump to output an operation fluid, a first hydraulic apparatus to be activated by the operation fluid, a second hydraulic apparatus other than the first hydraulic apparatus, the second hydraulic apparatus being configured to be activated by the operation fluid, a first operation valve to control the operation fluid to be supplied to the first hydraulic apparatus, a second operation valve to control the operation fluid to be supplied to the second hydraulic apparatus, a first fluid tube connecting the first operation valve to the first hydraulic apparatus, a second fluid tube connecting the first operation valve to the second hydraulic apparatus, a third fluid tube connecting the first fluid tube to the second fluid tube, and an outputting fluid tube connected to any one of the first operation valve and the second operation valve and configured to output the operation fluid supplied from any one of the first fluid tube and the second fluid tube.

BRIEF DESCRIPTION OF THE DRAWINGS

A more complete appreciation of the invention and many of the attendant advantages thereof will be readily obtained as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings, wherein:

FIG. 1 is a view illustrating a traveling hydraulic system (a hydraulic circuit) for a working machine according to a first embodiment of the present invention;

FIG. 2 is a view illustrating an operating hydraulic system (a hydraulic circuit) for the working machine according to the first embodiment;

FIG. 3A is a partially-enlarged view illustrating the traveling hydraulic system for the working machine according to the first embodiment;

FIG. 3B is a view illustrating a first modified example of the traveling hydraulic system illustrated in FIG. 3A according to the first embodiment;

FIG. 3C is a view illustrating a second modified example of the traveling hydraulic system illustrated in FIG. 3B according to the first embodiment;

FIG. 3D is a view illustrating a third modified example of the traveling hydraulic system illustrated in FIG. 3A according to the first embodiment;

FIG. 4 is a partially-enlarged view illustrating a traveling hydraulic system for a working machine according to a second embodiment of the present invention;

FIG. 5 is a view illustrating a relation between an engine revolution speed and a traveling primary pressure according to the second embodiment;

FIG. 6 is a side view illustrating a track loader as one example of the working machine according to the embodiments; and

FIG. 7 is a side view illustrating a part of the track loader lifting up a cabin according to the embodiments.

DESCRIPTION OF THE EMBODIMENTS

The embodiments will now be described with reference to the accompanying drawings, wherein like reference numerals designate corresponding or identical elements throughout the various drawings. The drawings are to be viewed in an orientation in which the reference numerals are viewed correctly.

Referring to drawings, the embodiments of the present invention, a hydraulic system for a working machine 1 and the working machine 1 having the hydraulic system, will be described below.

First Embodiment

A working machine will be explained below.

FIG. 6 shows a side view of the working machine 1 according to the embodiments of the present invention. FIG. 6 shows a compact track loader as an example of the working machine 1. However, the working machine 1 according to the embodiments is not limited to the compact track loader. The working machine 1 may be other types of the working machine such as a Skid Steer Loader (SSL). In addition, the working machine 1 may be other types of the working machine other than a loader working machine.

As shown in FIG. 6 and FIG. 7, the working machine 1 according to embodiments of the present invention includes a machine body (a vehicle body) 2, a cabin 3, an operation device 4, and a traveling device 5.

Hereinafter, in explanations of all the embodiments of the present invention, a forward direction (a left side in FIG. 6) corresponds to a front side of an operator seated on an operator seat 8 of the working machine 1, a backward direction (a right side in FIG. 6) corresponds to a back side of the operator, a leftward direction (a front surface side of the sheet of FIG. 6) corresponds to a left side of the operator, and a rightward direction (a back surface side of the sheet of FIG. 6) corresponds to a right side of the operator. Additionally in the explanations, a machine width direction corresponds to a horizontal direction (a lateral direction) perpendicular to the front to rear direction. A machine outward direction corresponds to a direction from a center portion of the machine body 2 to the right portion of the machine body 2 and to the left portion of the machine body 2.

In other words, the machine outward direction corresponds to the machine width direction, especially corresponds to a direction separating from the machine body 2. In the explanation, a machine inward direction corresponds to a direction opposite to the machine outward direction. In other words, the machine inward direction corresponds to the machine width direction, especially corresponds to a direction approaching the machine body 2 from the outside of the machine body 2.

The cabin 3 is mounted on the machine body 2. The operator seat 8 is disposed inside the cabin 3. The operation device 4 is constituted of a device configured to perform the working, the operation device 4 being attached to the machine body 2. The traveling device 5 is disposed on the outside of the machine body 2. A prime mover (an engine or an electric motor) 32 is mounted on a rear portion of the machine body 2 internally. The prime mover 7 is constituted of a diesel engine (that is, an engine). Meanwhile, the prime mover 7 is not limited to the engine, and may be constituted of an electric motor or the like.

The operation device 4 includes booms 10, a working tool 11, lift links 12, control links 13, boom cylinders 14, and bucket cylinders 15.

The operation device 4 includes two booms 10; one of the booms 10 is provided on a right side of the cabin 3 (referred to as the right boom 10) and is capable of freely swinging upward and downward, and the other one of the booms 10 is provided on a left side of the cabin 3 (referred to as the left boom 10) and is capable of freely swinging upward and downward. The working tool 11 is a bucket (hereinafter referred to as a bucket 11), for example. The bucket 11 is disposed on tip portions (front end portions) of the booms 10 and is capable of being freely swung upward and downward.

The lift link 12 and the control link 13 support a base portion (a rear portion) of the boom 10 such that the boom 10 is capable of being freely swung upward and downward. The boom cylinder 14 is capable of being stretched and shortened to move the boom 10 upward and downward. The bucket cylinder 15 is capable of being stretched and shortened to swing the bucket 11.

The operation device 4 includes two lift links 12, two control links 13, and two boom cylinders 14. One of the lift links 12 (the right lift link 12), one of the control links 13 (the right control link 13), and one of the boom cylinders 14 (the right boom cylinder 14) are disposed on a right side of the machine body 2, corresponding to the right boom 10. And, the other one of the lift links 12 (the left lift link 12), the other one of the control links 13 (the left control link 13), and the other one of the boom cylinders 14 (the left boom cylinder 14) are disposed on a left side of the machine body 2, corresponding to the left boom 10.

The lift link 12 is vertically disposed on a rear portion of the base portion of the boom 10. The lift link 12 is pivotally supported at an upper portion (one end side) of the lift link 12 by an upper portion of a base portion of the boom 10.

In addition, the lift link 12 is pivotally supported at a lower portion (the other end side) of the lift link 12 by a pivotal shaft (a second pivotal shaft) 17 to be close to a rear portion of the machine body 2, and is capable of freely turning about a lateral axis of the pivotal shaft 17. The second pivotal shaft 17 is arranged below the first pivotal shaft 16.

The boom cylinder 14 is pivotally supported at an upper portion of the boom cylinder 14 by a pivotal shaft (a third pivotal shaft) 18, and is capable of freely turning about a lateral axis of the third pivotal shaft 18. The third pivotal shaft 18 is arranged on each of base portions of the booms 10, specifically on a front portion of the base portion. The boom cylinder 14 is pivotally supported at a lower portion of the boom cylinder 14 by a pivotal shaft (a fourth pivotal shaft) 19, and is capable of freely turning about a lateral axis of the pivotal shaft 19. The fourth pivotal shaft 19 is arranged below the third pivotal shaft 18 to be close to a lower portion of the rear portion of the machine body 2.

The control link 13 is arranged forward from the lift link 12. One end of the control link 13 is pivotally supported by a pivotal shaft (a fifth pivotal shaft) 20, and is capable of freely turning about a lateral axis of the pivotal shaft 20. The fifth pivotal shaft 20 is disposed on the machine body 2, specifically on a position in front of and corresponding to the lift link 12.

The other end of the control link 13 is pivotally supported by a pivotal shaft (a sixth pivotal shaft) 21, and is capable of freely turning about a lateral axis of the pivotal shaft 21. The fifth pivotal shaft 21 is disposed on the boom 10, specifically in front of the second pivotal shaft 17 and above the second pivotal shaft 17.

The boom cylinder 14 is stretched and shortened, and thereby each of the booms 10 is swung upward and downward about the first pivotal shaft 16 with the base portion of each of the booms 10 supported by the lift link 12 and the control link 13. In this manner, the tip end portion of each of the booms 10 is moved upward and downward. The control link 13 is swung upward and downward about the fifth pivotal shaft 20 in accordance with the upward swing and downward swing of the booms 10. The lift link 12 is swung forward and backward about the second pivotal shaft 17 in accordance with the upward swing and downward swing of the control link 13.

Not only the bucket 11, other working tools can be attached to the tip end (the front portion) of the boom 10. The following attachments (spare attachments) are exemplified as the other working tools; for example, a hydraulic crusher, a hydraulic breaker, an angle broom, an earth auger, a pallet fork, a sweeper, a mower, a snow blower, and the like.

A connecting member 50 is disposed on the front portion of the boom 10 arranged to the left.

A hydraulic apparatus is installed on the auxiliary attachment. The connecting member 50 is a device configured to connect the hydraulic apparatus to a first tube member such as a pipe disposed on the boom 10. In particular, the first tube member is configured to be connected to one of the connecting member 50. A second tube member is connected to the hydraulic apparatus of the auxiliary attachment. The second tube member is configured to be connected to the other end of the connecting member 50. In this manner, the operation fluid flowing in the first tube member is supplied to the hydraulic apparatus through the second tube member.

The bucket 15 is arranged close to each of the front portions of the booms 10. The bucket cylinder 15 is stretched and shortened, and thereby the bucket 11 is swung.

In the embodiment, each of the travel device 5 arranged to the left and the travel device 5 arranged to the right employs a crawler travel device (including a semi-crawler travel device). However, each of the travel device 5A and the travel device 5B may employ a wheeled travel device having a front wheel and a rear wheel.

Next, the hydraulic system for the working machine 1 according to a first embodiment of the present invention will be described. The hydraulic system for the working machine 1 has a traveling hydraulic system and an operating hydraulic system.

As shown in FIG. 1, the traveling hydraulic system is a system configured to drive the traveling device 5, and includes a prime mover 32, a first hydraulic pump (a hydraulic pump) P1, a first traveling motor mechanism 31L, a second traveling motor mechanism 31R, and a traveling driving circuit 34.

The prime mover 32 is constituted of an electric motor, an engine, or the like. In this embodiment, the prime mover 32 is constituted of an engine. The first hydraulic pump P1 is constituted of a pump configured to be driven by the power of the prime mover 32, and is constituted of a constant displacement gear pump. The first hydraulic pump P1 is configured to output the operation fluid stored in the tank (operation fluid tank) 22.

An outputting fluid tube 40 through which the operation fluid flows is disposed on the outputting side of the first hydraulic pump P1. In the embodiments of the present invention, the fluid tube serves as an oil passage (also referred to as an operation fluid tube). A filter 35 is disposed on the intermediate portion of the outputting fluid tube 40. The outputting fluid tube 40 is branched into a plurality of sections on the outputting side of the operation fluid. A first charging fluid tube 41 is connected to the outputting side of the outputting fluid tube 40.

The first charging fluid tube 41 reaches the traveling drive mechanism 34. Of the hydraulic fluid outputted from the first hydraulic pump P1, the hydraulic fluid used for control may be referred to as pilot fluid, and the pressure of pilot fluid may be referred to as a pilot pressure.

The traveling drive mechanism 34 is a mechanism configured to drive the first traveling motor mechanism 31L and the second traveling motor mechanism 31R, and includes a driving circuit (a left driving circuit) 34L configured to drive the first traveling motor mechanism 31L and a driving circuit (a right driving circuit) 34R configured to drive the second traveling motor mechanism 31R.

The driving circuits 34L and 34R have HST pumps (the traveling pumps) 52L and 52R, the speed-changing fluid tubes (the transmission fluid tubes) 57h and 57i, and a second charging fluid tube 42, respectively. The speed-changing fluid tubes (the transmission fluid tubes) 57h and 57i are fluid tubes (fluid tubes) connecting the HST pumps 52L and 52R to the HST motor 36.

The second charging fluid tube 42 is a fluid tube (a fluid tube) connected to the speed-changing fluid tubes 57h and 57i and configured to charging the operation fluid outputted from the first hydraulic pump P1 to the speed-changing fluid tubes 57h and 57i. Each of the HST pumps 52L and 52R is constituted of a variable displacement axial pump having a swash plate, the variable displacement axial pump being configured to be driven by the motive power of the prime mover 32.

Each of the HST pumps 52L and 52R has a forward pressure-receiving portion 52a to which the pilot pressure is applied and a backward pressure-receiving portion 52b to which the pilot pressure is applied. And, the angle of the swash plate is changed by the pilot pressure applied to the pressure-receiving portions 52a and 52b. By changing the angle of the swash plate, it is possible to change an output (an output amount of the operation fluid) of the HST pumps 52L and 52R and an output direction of the operation fluid.

In other words, each of the HST pumps 52L and 52R changes the angle of the swash plate, and thereby changes the driving force outputted to the traveling device 5.

The first traveling motor mechanism 31L is a mechanism configured to transmit a power to the drive shaft of the traveling device 5 disposed on the left side of the machine body 2. The second traveling motor mechanism 31R is a mechanism configured to transmit a power to a drive shaft of the traveling device 5 disposed on the right side of the machine body 2. The first traveling motor mechanism 31L has an HST motor 36 (the traveling motor) 36 and a speed-changing mechanism.

The HST motor 36 is constituted of a variable displacement axial motor having a swash plate, the variable displacement axial being constituted of a motor configured to change a vehicle speed (a revolution speed) to a first speed or a second speed. In other words, the HST motor 36 is constituted of a motor configured to change a thrust power of the working machine 1.

The speed-changing mechanism includes a swash plate switching cylinder 38a and a travel switching valve 38b. The swash plate switching cylinder 38a is constituted of a cylinder configured to be stretched and shortened to change the angle of the swash plate of the HST motor 36. The travel switching valve 38b is constituted of a valve configured to stretch and shorten the swash plate switching cylinder 38a to one side of the swash plate switching cylinder 38a or the other side, specifically a two-position switching valve having a first position 39a and a second position 39b and being configured to be switched between the first position 39a and the second position 39b. The travel switching valve 38b is switched by a speed-changing switching valve 81a.

The speed-changing switching valve 81a is connected to the outputting fluid tube 40 and is connected to the travel switching valve 38b of the first traveling motor mechanism 31L and to the travel switching valve 38b of the second traveling motor mechanism 31R. The speed-changing switching valve 81a is constituted of a two-position switching valve having a first position 81a1 and a second position 81a2 and being configured to be switched between the first position 81a1 and the second position 81a2. When the speed-changing switching valve 81a is set to the first position 81a1, the pressure of the hydraulic fluid applied to the travel switching valve 38b of the speed-changing mechanism is set to a pressure corresponding to a predetermined speed (for example, the first speed).

In addition, when the speed-changing switching valve 81a is set to the first position 81a1, the pressure of the hydraulic fluid applied to the travel switching valve 38b is set to a pressure corresponding to a speed (the second speed) faster than being set to the pressure corresponding to the predetermined speed (the first speed). Thus, when the speed-changing switching valve 81a is in the first position 81a1, the travel switching valve 38b is set to the first position 39a, and thereby the swash plate switching cylinder 38a is shortened to set the HST motor 36 to the first speed.

In addition, when the speed-changing switching valve 81a is in the second position 81a2, the travel switching valve 38b is in the second position 39b, and accordingly the swash plate switching cylinder 38a is stretched thereby to shift the HST motor 36 to the second speed. Meanwhile, the HST motor 36 is shifted to the first speed and to the second speed under the control of the control device 90.

For example, the control device 90 is provided with an operation member 58 such as a switch (a speed-changing switch). When the operation member 58 is switched to the first speed, the control device 90 outputs a control signal for demagnetizing the solenoid of the speed-changing switching valve 81a and thereby switches the speed-changing switching valve 81a to the first position 81a1. In addition, when the operation member 58 is switched to the second speed, the control device 90 outputs a control signal for magnetizing the solenoid of the speed-changing switching valve 81a and thereby switches the speed-changing switching valve 81a to the second position 81a2.

In addition, the first traveling motor mechanism 31L has a brake mechanism 30. The brake mechanism 30 is configured to brake the traveling device 5 disposed to the right, that is, to stop the rotation of the HST motor 36 or the rotation of the output shaft rotating in accordance with the rotation of the HST motor 36. Due to the pilot fluid (the operation fluid) outputted from the first hydraulic pump P1, the brake mechanism 30 shifts to an operating state in which the traveling motor mechanism 31 is braked or to an operating state in which the braking is released.

For example, the brake mechanism 30 includes a first disk disposed on the output shaft of the traveling motor mechanism 31, a second disk configured to be movable, and a spring configured to push the second disk toward the first disk. In addition, the brake mechanism 30 is provided with a housing portion (a housing case) 59 configured to house the first disc, the second disc, and the spring. In the housing portion 59, a portion in which the second disc is stored is connected to a brake switching valve 80a by a fluid tube as described below.

The brake switching valve 80a is constituted of a solenoid valve configured to carry out the braking and the release of braking (the brake releasing) in the brake mechanism 30, that is, a two-position switching valve configured to be switchable between a first position 80a1 and a second position 80a2. When the brake switching valve 80a is in the first position 80a1, the brake switching valve 80a regulates the pressure of the operation fluid to be applied to the brake mechanism 30 (the pressure applied to the housing portion 59) to the pressure at which the brake mechanism 30 carries out the braking. In addition, when the brake switching valve 80a is in the second position 80a2, the brake switching valve 80a is set to regulate the operation fluid to a pressure for the brake releasing.

The switching of the brake switching valve 80a is carried out under the control of the control device 90. For example, the controller 90 outputs a control signal for demagnetizing the solenoid of the brake switching valve 80a, and thereby sets the brake switching valve 80a to the first position 80a1.

In addition, the control device 90 outputs a control signal for magnetizing the solenoid of the brake switching valve 80a, and thereby sets the brake switching valve 80a to the second position 80a2. Further, the control device 90 may outputs the control signal to the brake switching valve 80a, for example, with use of a preliminarily-provided switch and with manually operating the switch. And, the control device 90 may automatically output the control signal through judgment of the driving situation of the working machine 1.

Thus, when the brake control valve 80a is in the first position 80a1, the pilot fluid in the storage portion of the housing portion 59 is outputted, the second disk moves in the direction of the braking, and thereby the braking is carried out in the brake mechanism 30. In addition, when the brake control valve 80a is in the second position 80a2, the pilot fluid is supplied to the storage portion of the housing portion 59, the second disk moves in a direction opposite to the direction of the braking (in a direction opposite to the biasing direction of the spring), and thereby the braking is released in the brake mechanism 30.

Meanwhile, since the second traveling motor mechanism 31R has the same configuration as that of the first traveling motor mechanism 31L, the configuration described in the first traveling motor mechanism 31L may be applied to the second traveling motor mechanism 31R. Thus, the explanation of the configurations will be omitted.

As shown in FIG. 1, the working machine 1 includes an operation device 53. The operation device 53 is a device configured to operate the traveling device 5, that is, the first traveling motor mechanism 31L, the second traveling motor mechanism 31R, and the travel driving circuit 34. The operation device 53 has a first operation member 54 and a plurality of operation valves 55 (55a, 55b, 55c, and 55d).

The first operation member 54 is an operation member that is supported by the operation valve 55 and is swung in the left-to-right direction (the machine width direction) or in the front-to-rear direction. In addition, the plurality of operation valves 55 are operated commonly, that is, by one first operation member 54. The plurality of operation valves 55 operate based on the swing of the first operation member 54. The operation fluid (the pilot fluid) can be supplied from the first hydraulic pump P1 to the plurality of operation valves 55 through the outputting fluid tube 40. The plurality of operation valves 55 includes the operation valve 55a, the operation valve 55b, the operation valve 55c, and the operation valve 55d.

The plurality of operation valves 55 and the traveling drive mechanism 34 for the traveling (the travel pumps 52L and 52R) are connected by a traveling fluid tube 45. The traveling fluid tube 45 includes a first traveling fluid tube 45a, a second traveling fluid tube 45b, a third traveling fluid tube 45c, a fourth traveling fluid tube 45d, and a fifth traveling fluid tube 45e. The first traveling fluid tube 45a is constituted of a fluid tube connected to the forward pressure-receiving portion 52a of the traveling pump 52L.

The second traveling fluid tube 45b is constituted of a fluid tube connected to the backward pressure-receiving portion 52b of the traveling pump 52L. The third traveling fluid tube 45c is constituted of a fluid tube connected to the forward pressure-receiving portion 52a of the travel pump 52R. The fourth traveling fluid tube 45d is constituted of a fluid tube connected to the backward pressure-receiving portion 52b of the traveling pump 52R.

The fifth traveling fluid tube 45e is constituted of a fluid tube connecting the operation valve 55, the first traveling fluid tube 45a, the second traveling fluid tube 45b, the third traveling fluid tube 45c, and the fourth traveling fluid tube 45d to each other. The fifth traveling fluid tube 45e connects a plurality of shuttle valves 46 and the plurality of operation valves 55 (55a, 55b, 55c, 55d) to each other.

When the first operation member 54 is swung forward (in the direction indicated by an arrowed line A1 in FIG. 1), the operation valve 55a is operated, and thereby the pilot pressure is outputted from the operation valve 55a. In this manner, the output shaft of the traveling motor 36 revolves forward at a speed proportional to a swinging amount (a swinging extent) of the first operation member 54, and thus the working machine 1 travels straight forward.

In addition, when the first operation member 54 is swung backward (in the direction indicated by an arrowed line A2 in FIG. 1), the operation valve 55b is operated, and thereby the pilot pressure is outputted from the operation valve 55b. In this manner, the output shaft of the traveling motor 36 revolves backward at a speed proportional to a swinging amount (a swinging extent) of the first operation member 54, and thus the working machine 1 travels straight backward.

In addition, when the first operation member 54 is swung to the right (the direction indicated by an arrowed line A3 in FIG. 1), the operation valve 55c is operated to output the pilot pressure from the operation valve 55c, and thereby the output shaft of the traveling motor 36 on the left side rotates in the forward direction, the output shaft of the running motor 36 on the right side rotates in the reverse direction, and thereby the working machine 1 turns to the right.

When the first operation member 54 is swung to the left (the direction indicated by an arrowed line A4 in FIG. 1), the operation valve 55d is operated to output the pilot pressure from the operation valve 55d, and thereby the output shaft of the traveling motor 36 on the left side rotates in the reverse direction, the output shaft of the running motor 36 on the right side rotates in the forward direction, and thereby the working machine 1 turns to the left.

In addition, when the first operation member 54 is swung in the oblique direction, the differential pressure between the pilot pressure applied to the pressure-receiving portion 52a and the pilot pressure applied to the pressure-receiving portion 52b determines the rotation directions and the rotation speeds of the output shafts of the traveling motor 36 on the left and the traveling motor 36 on the right, and thereby the working machine 1 turns rightward or leftward while moving forward or backward.

Next, the operating hydraulic system will be described below.

As shown in FIG. 2, the operating hydraulic system is a system configured to operate the boom 10, the bucket 11, the auxiliary attachment and the like, and includes a plurality of control valves 51 and an operating hydraulic pump (a second hydraulic pump P2).

The second hydraulic pump P2 is arranged on a position different from the position of the first hydraulic pump P1, and is constituted of a low-displacement gear pump. The second hydraulic pump P2 is configured to output the operation fluid stored in the operation fluid tank. In particular, the second hydraulic pump P2 outputs the operation fluid mainly used for the operation of the hydraulic actuator.

On the outputting side of the second hydraulic pump P2, an operation fluid tube 51f is disposed. A plurality of control valves 51 are connected to the operation fluid tube 51f. The boom control valve 51a is constituted of a valve configured to control the boom cylinder 14, the bucket control valve 51b is a valve configured to control the bucket cylinder 15, and the auxiliary control valve 51c is a valve configured to control the hydraulic actuator of the auxiliary attachment.

The operation of the boom 10 and the bucket 11 are operated by the second operation member 37 connected to the operation device 43. The second operation member 37 is constituted of an operation member supported by the operation valve 23 and configured to swing in the lateral direction (the machine width direction) or in the front-to-rear direction. By tilting the second operation member 37, each of the operation valves 23 arranged on the lower portion of the second operation member 37 is operated.

When the second operation member 37 is tilted forward and backward, the downward-moving operation valve 23a is operated to output the pilot pressure from the downward-moving operation valve 23a. The pilot pressure applied to the pressure-receiving portion of the boom control valve 51a, the hydraulic fluid entering the boom control valve 51a is supplied to the rod side of the boom cylinder 14, and thereby the boom 10 is moved downward.

When the second operation member 37 is tilted backward, the upward-moving operation valve 23b is operated to output the pilot pressure from the upward-moving operation valve 23b. The pilot pressure is applied to the pressure-receiving portion of the boom control valve 51a, the operation fluid entering the boom control valve 51a is supplied to the bottom side of the boom cylinder 14, and thereby the boom 10 is moved upward.

That is, the boom control valve 51a is configured to control the flow rate of the hydraulic fluid flowing through the boom cylinder 14 in accordance with the pressure of the operation fluid set by the operation of the second operation member 37 (the pilot pressure set by the downward-moving operation valve 23a and the pilot pressure set by the upward-moving operation valve 23b).

When the second operation member 37 is tilted rightward, the operation valve 23c for the bucket dumping is operated, and thereby the pilot pressure is applied to the pressure-receiving portion of the bucket control valve 51b. As the result, the bucket control valve 51b operates in a direction to stretch the bucket cylinder 15, and thereby the bucket 11 performs the dumping movement at a speed proportional to the tilting amount of the second operation member 37.

When the second operation member 37 is tilted leftward, the operation valve 23d for the bucket shoveling is operated, and thereby the pilot fluid is applied to the pressure-receiving portion of the bucket control valve 51b. As the result, the bucket control valve 51b operates in a direction to shorten the bucket cylinder 15, and thereby the bucket 11 performs the shoveling operation at a speed proportional to the tilting amount of the second operation member 37.

In other words, the bucket control valve 51b controls the flow rate of the operation fluid flowing through the bucket cylinder 15 in accordance with the pressure of the operation fluid set by the operation of the second operation member 37 (the pilot pressure set by the operation valve 23c and the pilot pressure set by the operation valve 23d). That is, the operation valves 23a, 23b, 23c, and 23d change the pressure of the hydraulic fluid in accordance with the operation of the second operation member 37 and thereby supply the hydraulic fluid already changed to the control valves such as the boom control valve 51a, the bucket control valve 51b, and the auxiliary control valve 51c.

The operation of the auxiliary attachment is carried out by a switch 56 disposed around the operator seat 8. The switch 56 is constituted of, for example, a swingable seesaw type switch, a slidable slide type switch, or a pressable push type switch. The operation of the switch 56 is inputted to the control device 90. The first solenoid valve 56a and the second solenoid valve 56b each composed of solenoid valves and the like are opened in accordance with the operation amount of the switch 56.

As the result, the pilot fluid is supplied to the auxiliary control valve 51c, the auxiliary control valve 51c being connected to the first solenoid valve 56a and the second solenoid valve 56b. And, the auxiliary actuator of the auxiliary attachment is operated by the hydraulic fluid supplied from the auxiliary control valve 51c.

Meanwhile, the hydraulic system for the working machine 1 connects the first fluid tube connected to the first hydraulic apparatus to the second fluid tube connected to the second hydraulic apparatus with the third fluid tube, and thereby helping the warming-up. In this embodiment, the first fluid tube, the second fluid tube, and the third fluid tube will be described on the assumption that the first hydraulic apparatus is constituted of a brake mechanism 30 and a speed-changing mechanism.

As shown in FIG. 1 and FIG. 3A, the first fluid tube 61 is constituted of a fluid tube connecting a first hydraulic apparatus (the brake mechanism 30) to a first operation valve (the brake switching valve) 80a for controlling the operation fluid supplied to the first hydraulic apparatus (the brake mechanism 30). In this embodiment, the first fluid tube 61 includes a first brake fluid tube 61a and a second brake fluid tube 61b.

The first brake fluid tube 61a is constituted of a fluid tube connecting the brake mechanism 30 of the first traveling motor mechanism 31L to the brake switching valve (the first operation valve) 80a. The second brake fluid tube 61b is constituted of a fluid tube connecting the brake mechanism 30 of the second traveling motor mechanism 31R to the brake switching valve (the first operation valve) 80a. The first brake fluid tube 61a and the second brake fluid tube 61b are confluent with each other in the intermediate portion, and a fluid tube 61c after the confluent portion (that is, a fluid tube (a shared fluid tube) shared with both of the first brake fluid tube 61a and the second brake fluid tube 61b) is connected to a brake switching valve 80a.

The shared fluid tube 61c is provided with a throttling portion 74 configured to reduce the flow rate of the operation fluid. In other words, the throttling portion 74, in the first fluid tube 61a, is connected to a section between a connecting portion (that is, a confluent portion 64 described below) where the third fluid tube 63 is connected to the first fluid tube 61 and another connecting portion connected to the throttle portion 80a.

The output port of the brake switching valve 80a is connected to an outputting fluid tube 66 configured to output the operation fluid of the first fluid tube 61 (the first brake fluid tube 61a and the second brake fluid tube 61b). The outputting fluid tube 66 is connected to the suction port of the hydraulic pump, to the operation fluid tank 22, and the like.

The second fluid tube 62 is constituted of a fluid tube connecting the second hydraulic device (the speed-changing mechanism) to the second operation valve (the speed-changing switching valve) 81a configured to control the operation fluid, the operation fluid being supplied to the first hydraulic apparatus (the speed-changing mechanism). In this embodiment, the second fluid tube 62 includes a first speed-changing fluid tube 62a and a second speed-changing fluid tube 62b.

The first speed-changing fluid tube 62a is constituted of a fluid tube connecting the speed-changing switching valve (the second operation valve) 81a to the travel switching valve 38b of the speed-changing mechanism in the first traveling motor mechanism 31L. The second speed-changing fluid tube 62b is constituted of a fluid tube connecting the speed-changing switching valve (the second operation valve) 81a to the travel switching valve 38b of the speed-changing mechanism in the second traveling motor mechanism 31R.

The first speed-changing fluid tube 62a and the second speed-changing fluid tube 62b are confluent with each other in the intermediate portion, and a fluid tube after the confluent portion is connected to a speed-changing switching valve 81a. The output port of the speed-changing switching valve 81a is connected to an outputting fluid tube 67 configured to output the operation fluid of the second fluid tube 62 (the first speed-changing fluid tube 62a and the second speed-changing fluid tube 62b). The outputting fluid tube 67 is connected to the suction port of the hydraulic pump, to the operation fluid tank 22, and the like.

The third fluid tube 63 is constituted of a fluid tube connecting the first fluid tube 61 and the second fluid tube 62 to each other. The third fluid tube 63 connects, to each other, a confluent portion 64 where the first brake fluid tube 61a and the second brake fluid tube 61b are confluent with each other and a confluent portion 65 where the first speed-changing fluid tube 62a and the second speed-changing fluid tube 62b are confluent with each other. The third fluid tube 63 is provided with a throttling portion 73 configured to reduce the flow rate of the operation fluid.

As described above, when the speed-changing switching valve (the second operation valve) 81a is set to the first speed and the brake switching valve 80a is set to the second position 80a2 for example, the hydraulic fluid in the first fluid tube 61 flows to the second fluid tube 62 through the third fluid tube 63 and is outputted from the output port of the speed-changing switching valve 81a to the outputting fluid tube 67. Thus, it is possible to warm up the first fluid tube (the brake fluid tube) and the second fluid tube (the speed-changing fluid tube).

That is, the first fluid tube 61 and the second fluid tube 62 are connected to each other by the third fluid tube 63, the first fluid tube 61 connecting the brake switching valve 80a and the brake mechanism 30 to each other, the second fluid tube 62 connecting the speed-changing switching valve 81a and the speed-changing mechanism (the travel switching valve 38b) to each other. Then, the outputting fluid tubes 66 and 67 are provided, the outputting fluid tubes 66 and 67 being configured to output the hydraulic fluid from any one of the first fluid tube 61 and the second fluid tube 62, and thereby it is possible to easily warm up the first fluid tube 61 and the second fluid tube 62.

In particular, the brake switching valve 80a is constituted of a switching valve configured to be switched between the first position 80a1 and the second position 80a2, and the speed-changing switching valve 81a is constituted of a switching valve configured to be switched between the first position 81a1 and the second position 81a2. In this manner, the warming-up is simply carried out by switching both of the switching valves.

For example, the control device 90 controls the first operation valve 80a and the second operation valve 81a, and thereby introduces the operation fluids of the first fluid tube 61 and the second fluid tube 62 to the outputting fluid tube through the third fluid tube, thereby warming up the hydraulic fluid. When the warming up of the hydraulic fluid is carried out, the control device 90 switches the speed-changing switching valve (the second operation valve) 81a to the first position 81a1, and switches the brake switching valve (the first operation valve) 80a to the second position 80a2.

In this manner, the hydraulic fluid in the first fluid tube 61 flows to the second fluid tube 62 through the third fluid tube 63, and is outputted from the output port of the speed-changing switching valve 81a to the outputted fluid tube 67, and thereby the operation fluid is warmed up while the working machine 1 travels at the first speed.

FIG. 3B is a view showing a first modification example of the hydraulic system shown in FIG. 3A. Meanwhile, for convenience of the explanation, FIG. 3B shows the fluid tubes (the first brake fluid tube 61a and the first speed-changing fluid tube 62a) disposed on the side of the first traveling motor mechanism 31L, and the fluid tubes (the second brake fluid tube 61b and the second speed-changing fluid tube 62b) disposed on the side of the second traveling motor mechanism 31R are omitted. The configuration of the fluid tubes (the first brake fluid tube 61a and the first speed-changing fluid tube 62a) disposed on the side of the first traveling motor mechanism 31L may be employed in the fluid tube disposed on the side of the second traveling motor mechanism 31R.

As shown in FIG. 3B, the first modification describes an example in which the travel switching valve (the second operation valve) 81a is replaced by a speed-changing proportional valve 81b, the speed-changing proportional valve 81b being constituted of an electromagnetic proportional valve. The control of the speed-changing proportional valve 81b is carried out by the control of the control device 90. For example, when the operation member 58 is switched to the first speed, the control device 90 outputs a control signal to the speed-changing proportional valve 81b, and thereby sets the opening aperture of the speed-changing proportional valve 81b to the opening aperture corresponding to the first speed.

In other words, the speed-changing proportional valve 81b sets the pressure of the hydraulic fluid applied to the travel switching valve 38b (the pressure applied to the pressure-receiving portion of the travel switching valve 38b) to a pressure required to keep the travel switching valve 38b in the first position 81a1. When the operation member 58 is switched to the second speed, the control device 90 outputs a control signal to the speed-changing proportional valve 81b, and thereby sets the opening aperture of the speed-changing proportional valve 81b to be larger than the opening aperture corresponding to the first speed.

That is, the speed-changing proportional valve 81b sets the pressure of the hydraulic fluid applied to the travel switching valve 38b (the pressure applied to the pressure-receiving portion of the travel switching valve 38b) to a pressure required to keep the travel switching valve 38b in the second position 81a2. That is, the speed-changing proportional valve 81b sets the pressure of the hydraulic fluid supplied to the travel switching valve 38b of the speed-changing mechanism to a pressure required to change the speed of the speed-changing mechanism.

The speed-changing proportional valve 81b has a primary port (a pump port) 81b1 and a secondary port 81b2. The primary port 81b1 of the speed-changing proportional valve 81b is connected to the outputting fluid tube 40. The secondary port 81b2 of the speed-changing proportional valve 81b is connected to the second fluid tube 62 (the first speed-changing fluid tube 62a and the second speed-changing fluid tube 62b). The output port 81b3 of the speed-changing proportional valve 81b is connected to the operation fluid tank 22 by an outputting fluid tube 67.

A first bypass fluid tube 68 is connected to the third fluid tube 63. The first bypass fluid tube 68 is provided with a first check valve 71. The first check valve 71 is constituted of a valve configured to allow the hydraulic fluid to flow from the second fluid tube 62 to the first fluid tube 61 and to block the hydraulic fluid from flowing from the first fluid tube 61 toward the second fluid tube 62.

The second bypass fluid tube 69 is connected to the first fluid tube 61 between the brake switching valve 80a and the third fluid tube 63. The second bypass fluid tube 69 is provided with a second check valve 72. The second check valve 72 is constituted of a valve configured to allow the hydraulic fluid to flow from the connecting portion between the first fluid tube 61 and the third fluid tube 63 to the brake switching valve 80a and to block the fluid tube from flowing from the brake switching valve 80a toward the connecting portion.

Meanwhile, the third fluid tube 63 is provided with the first bypass fluid tube 68 and the first check valve 71. However, the third fluid tube 63 may be not provided with the first bypass fluid tube 68 and the first check valve 71. In addition, the first fluid tube 61 is provided with the second bypass fluid tube 69 and the second check valve 72. However, the first fluid tube 61 may be not provided with the second bypass fluid tube 69 and the second check valve 72. Alternatively, the hydraulic system for the working machine 1 may include the first bypass fluid tube 68 and the first check valve 71 or include the second bypass fluid tube 69 and the second check valve.

As described above, In the case where the pressure at which the travel switching valve 38b is switched to the second position 81a2 is a pressure to set the second speed, the opening aperture of the speed-changing proportional valve 81b is set so that the pressure applied to the travel switching valve 38b does not exceed the pressure to set the second speed under the state where the brake switching valve 80a is set to the first position 80a1 and the brake mechanism 30 performs the braking.

In this manner, the hydraulic fluid of the second fluid tube 62 passes through the first bypass fluid tube 68 and the second bypass fluid tube 69 and then is outputted from the outputting fluid tube 66 connected to the brake switching valve 80a. For example, in the warming-up of the hydraulic fluid, the control device 90 switches the brake switching valve 80a to the first position 80a1, and then sets the opening aperture of the speed-changing proportional valve 81b so as not to switch the travel switching valve 38b to the second position 39b (sets the applied pressure to be less than the pressure to set the second speed).

In addition, in the case where the brake switching valve 80a is set to the second position 80a2 and then the brake mechanism 30 releases the braking, the opening aperture of the speed-changing proportional valve 81b is adjusted such that the pressure applied to the travel switching valve 38b by the speed-changing proportional valve 81b is equal to or more than the pressure to set the second speed and less than the pressure applied to the primary port 81b1 of the speed-changing proportional valve 81b.

For example, in the case where the pressure of the hydraulic fluid applied to the primary port 81b1 of the speed-changing proportional valve 81b is 2.8 MPa and the pressure to set the second speed is 1.0 MPa, the pressure of the hydraulic fluid applied to the secondary port 81b2 of the speed-changing proportional valve 81b is 1.8 MPa and the like. In this manner, the operation fluid of the first fluid tube 61 is supplied to the third fluid tube 63 and the second fluid tube 62, and thus is outputted from the outputting fluid tube 67 connected to the speed-changing proportional valve 81b.

For example, a first measuring device and a second measuring device are connected to the control device 90, the first measuring device being configured to measure a pressure (a first pressure) applied to the primary port 81b1 of the speed-changing proportional valve 81b, the second measuring device being configured to measure a pressure (a second pressure) applied to the secondary port 81b2 of the speed-changing proportional valve 81b.

For example, the first measuring device is disposed on the outputting fluid tube 40 in the vicinity of the brake switching valve 80a. In addition, the second measuring device is disposed on the second fluid tube 62. For example. it is preferred for the second fluid tube 62 to dispose the second measuring device in the vicinity of the pressure-receiving portion of the travel switching valve 38b. The first pressure is measured based on the distance from the first measuring device to the primary port 81b1 of the speed-changing proportional valve 81b and in accordance with the calculation a pressure loss of the outputting fluid tube 40 calculated by the control device 90 and the like with respect to the measured value measured by the first measuring device.

In addition, since the pressure on the primary side (the first pressure) can be estimated based on the revolution speeds of the first hydraulic pump P1, the engine, and the like, the first measuring device may be omitted. In addition, since the pressure on the operation fluid applied to the travel switching valve 38b can be estimated based on the operating condition such as the temperature of the operation fluid, the revolution speed of the engine, and the like, the second measuring device may be omitted.

In the warming-up of the hydraulic fluid, the control device 90 switches the brake switching valve 80a to the second position 80a2 and sets the opening aperture of the speed-changing proportional valve 81b. Here, in the case where the control device 90 sets the opening aperture of the speed-changing proportional valve 81b, the control device 90 sets the opening aperture of the speed-changing proportional valve 81b so that the first pressure is equal to or lower than the second pressure and the pressure applied to the travel switching valve 38b is equal to or higher than the pressure to set the second speed.

In addition, in the case where the brake switching valve 80a is set to the second position 80a2 and thus releases the braking carried out by the brake mechanism 30, the opening aperture of the speed-changing proportional valve 81b is adjusted so as to set the pressure applied to the travel switching valve 38b by the speed-changing proportional valve 81b to be less than the pressure to set the second speed and to be the pressure to set the first speed. In that case, the operation fluid of the first fluid tube 61 passes through the third fluid tube 63, and then is outputted from the outputting fluid tube 67 of the speed-changing proportional valve 81b.

For example, In the case where the hydraulic fluid is warmed up, the control device 90 switches the brake switching valve 80a to the first position 80a1 and adjusts the opening aperture of the speed-changing proportional valve 81b so as to set the travel switching valve 38b to be in the first position 39a.

FIG. 3C shows a second modification of the hydraulic system shown in FIG. 3B. As shown in FIG. 3C, the second modified example describes an example in which the brake switching valve (the first operation valve) 80a is replaced by an electromagnetic proportional valve (the brake switching valve) 80b.

In the case where the braking is released by the brake mechanism 30, the control device 90 outputs a control signal to the brake proportional valve 80b, and thereby sets the opening aperture of the brake proportional valve 80b to the opening aperture corresponding to the pressure (the brake releasing pressure) at which the brake mechanism 30 releases the braking. For example, in the case where the brake mechanism 30 carries out the braking, the control device 90 sets the opening aperture of the brake proportional valve 80b to the maximum extent (fully opens the brake proportional valve 80b).

Additionally, in the case where the brake mechanism 30 carries out the braking, the control device 90 outputs a control signal to the brake proportional valve 80b, and thereby sets the opening aperture of the brake proportional valve 80b to the opening aperture corresponding to the brake releasing pressure. For example, in the case where the brake mechanism 30 carries out the brake releasing, the control device 90 sets the opening aperture of the brake proportional valve 80b to the minimum extent (fully closes the brake proportional valve 80b).

The brake proportional valve 80b has a primary port (a pump port) 80b1 and a secondary port 80b2. The primary port 80b1 of the brake proportional valve 80b is connected to the outputting fluid tube 40. The secondary port 80b2 of the brake proportional valve 80b is connected to the first fluid tube 61. The outputting port 80b3 of the brake proportional valve 80b is connected to the operation fluid tank 22 through the outputting fluid tube 66.

As described above, the speed-changing proportional valve 81b is fully opened, and thereby the brake proportional valve 80b is set to be switched at a pressure equal to or higher than the brake releasing pressure and lower than the pressure applied to the primary port 80b1. In this manner, the operation fluid of the second fluid tube 62 is supplied to the third fluid tube 63 and then to the first fluid tube 61 sequentially, and then is outputted from the outputting fluid tube connected to the brake proportional valve 80b.

For example, a third measuring device and a fourth measuring device are connected to the control device 90, the third measuring device being configured to measure the pressure (a third pressure) applied to the primary port 80b1 of the brake proportional valve 80b, the fourth measuring device being configured to measure the brake releasing pressure. For example, the third measuring device is disposed in the vicinity of the pump port side of the speed-changing proportional valve 81b, and the fourth measuring device is disposed on the first fluid tube 61. In the case where the hydraulic fluid is warmed up, the control device 90 sets the opening aperture of the speed-changing proportional valve 81b to be fully opened, and thereby the opening aperture of the brake proportional valve 80b is set to provide the pressure of the operation fluid applied to the brake mechanism 30, the pressure being equal to or higher than the brake releasing pressure and equal to or lower than the third pressure.

In addition, in the case where the warming-up of the hydraulic fluid is carried out by the control device 90, the brake proportional valve 80b may be closed to set the braking state, and additionally the speed-changing proportional valve 81b may be opened. Also in that case, the operation fluid of the second fluid tube 62 is supplied to the third fluid tube 63 and then to the first fluid tube 61 sequentially, and then is outputted from the outputting fluid tube 66 connected to the brake proportional valve 80b.

In addition, FIG. 3D shows a third modified example of the hydraulic system shown in FIG. 3A. The third modified example provides the throttling portion 73 on the third fluid tube 63, provides the first bypass fluid tube 68 on the third fluid tube 63, and provides the first check valve 71 on the first bypass fluid tube 68 in the hydraulic circuit provided with the brake switching valve 80a and the speed-changing switching valve 81a. In addition, the throttling portion 83 is provided on a section between the speed-changing switching valve 81a and the confluent portion 65 in the second fluid tube 62a.

In that case, the control device 90 carries out the braking performed by the brake mechanism 30 and switches the speed-changing switching valve 81a to the second position 81a2, and thereby the hydraulic fluid of the second fluid tube 62 is supplied to the first bypass fluid tube 68 through the first check valve 71, and is outputted to the outputting fluid tube 66 of the brake switching valve 80a.

Second Embodiment

FIG. 4 shows a hydraulic system according to a second embodiment of the present invention. The traveling hydraulic system shown in the second embodiment can be employed in the hydraulic system according to the first embodiment described above, and is configured to be warmed up easily. Configurations similar to those of the first embodiment will be omitted.

In the hydraulic system according to the second embodiment, a control for preventing the engine stall (an anti-stalling control) is carried out. A proportional valve (hereinafter referred to as anti-stalling proportional valve) 82 is disposed on the outputting fluid tube 40, specifically on the path of the operating device 53, and the anti-stalling proportional valve 82 is controlled to carry out the anti-stalling control.

FIG. 5 shows the relation between the engine revolution speed, the traveling primary pressure, and the control lines L1 and L2. The traveling primary pressure is a pressure of the operation fluid (that is, the pilot pressure) in the section extending from the anti-stalling proportional valve 82 to the operation valves 55 (the operation valve 55a, the operation valve 55b, the operation valve 55c, and the operation valve 55d) in the outputting fluid tube 40.

That is, the traveling primary pressure is the primary pressure of the hydraulic fluid flowing into the operation valve 55 disposed on the operating lever 54. The control line L1 shows the relation between the engine revolution speed and the traveling primary pressure under the state where the dropping amount is less than a predetermined amount. The control line L2 shows the relation between the engine revolution speed and the traveling primary pressure under the state where the dropping amount is equal to or larger than the predetermined amount.

When the dropping amount is less than the predetermined amount, the control device 90 controls an opening aperture of the anti-stalling proportional valve 82 such that the relation between the actual revolution speed of the engine and the traveling primary pressure corresponds to the control line L1. In addition, when the dropping amount is equal to or larger than the predetermined value, the control device 90 controls the opening aperture of the anti-stalling proportional valve 82 so that the relation between the actual revolution speed of the engine and the traveling primary pressure corresponds to the control line L2.

In the control line L2, the traveling primary pressure for a predetermined engine revolution speed is lower than the traveling primary pressure of the control line L1. That is, when paying attention to the same engine speed, the traveling primary pressure of the control line L2 is lower than the traveling primary pressure of the control line L1. Thus, by the control based on the control line L2, the pressure (the pilot pressure) of the hydraulic fluid flowing into the operation valve 55 is suppressed to be low. As the result, the angle of the swash plate of the HST pump (the traveling pump) 52 is adjusted, a load applied to the engine is reduced, and thereby the stalling of the engine is prevented.

Meanwhile, FIG. 5 shows one control line L2. However, a plurality of the control lines L2 may be employed. For example, the control line L2 may be provided for each engine revolution speed. In addition, it is preferred that the control device 90 has data indicating the control lines L1 and control lines L2, control parameters such as functions, and the like.

The anti-stalling proportional valve 82 has a primary port (pump port) 82b1 and a secondary port 82b2. A primary port 82b1 of the anti-stalling proportional valve 82 is connected to an intermediate portion of the outputting fluid tube 40, and a secondary port 82b2 is connected to a section (40a) extending from the intermediate portion of the outputting fluid tube 40 to the operation valve 55 of the operation device 53 in the outputting fluid tube 40. An outputting fluid tube 67 is connected to the output port 82b3.

In the second embodiment, the first hydraulic apparatus is constituted of a brake mechanism 30, which is the HST pump 52, that is, the traveling drive mechanism 34. The first fluid tube 61 is a fluid tube configured to connect the brake mechanism 30 and the brake switching valve 80a to each other. And, as in the first embodiment, the first fluid tube 61 includes a first brake fluid tube 61a and a second brake fluid tube 61b. Meanwhile, in FIG. 4, only the first brake fluid tube 61a is shown for convenience of the explanation.

The second fluid tube 62 is a fluid tube configured to connect the HST pump 52 and the anti-stalling proportional valve 82 to each other. In this embodiment, the second fluid tube 62 includes a section 40a of the outputting fluid tube 40 and a traveling fluid tube 45. Meanwhile, in FIG. 4, a part of the traveling fluid tube 45 is shown for convenience of the explanation. One end of the third fluid tube 63 is connected to an intermediate portion of the first brake fluid tube 61a, and the other end of the third fluid tube is connected to an intermediate portion of the section 40a of the outputting fluid tube 40.

As described above, similarly to the relation between the switching of the brake switching valve 80a and the opening aperture (the pressure) of the speed-changing proportional valve 81b as described in the first embodiment, the relation between the switching of the brake switching valve 80a and the opening aperture (the pressure) of the anti-stalling proportional valve 82 is set. In this manner, the hydraulic fluid in the first fluid tube 61 or the second fluid tube 62 is allowed to be supplied to the output port of the brake switching valve 80a and to the output port of the anti-stalling proportional valve 82, and thereby the warming-up is carried out easily.

In the above description, the embodiment of the present invention has been explained. However, all the features of the embodiment disclosed in this application should be considered just as examples, and the embodiment does not restrict the present invention accordingly. A scope of the present invention is shown not in the above-described embodiment but in claims, and is intended to include all modifications within and equivalent to a scope of the claims.

In the above-described embodiments, the first measuring device to the fourth measuring device are employed, and the warming-up is carried out based on the measured values measured by the respective measuring devices. However, in place of that configuration, the control device 90 may store the opening apertures of the first operation valve and the second operation valve, the opening apertures being employed in the warming-up, and thereby may carry out the worming-up without the measurements by the first measuring device to the fourth measuring device.

Obviously, numerous modifications and variations of the present invention are possible in light of the above teachings. It is therefore to be understood that within the scope of the appended claims, the invention may be practiced otherwise than as specifically described herein.

Number	Date	Country	Kind
2016-255461	Dec 2016	JP	national
2017-227076	Nov 2017	JP	national

HYDRAULIC SYSTEM FOR WORKING MACHINE

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CPC

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Priority Claims (2)