WO2023095739A1

WO2023095739A1 - Hydraulic system for industrial vehicle

Info

Publication number: WO2023095739A1
Application number: PCT/JP2022/042973
Authority: WO
Inventors: 裕康小寺; 政浩松尾; 崇三木; 祐介藤本
Original assignee: 川崎重工業株式会社
Priority date: 2021-11-24
Filing date: 2022-11-21
Publication date: 2023-06-01
Also published as: JP2023076907A; CN118103573A

Abstract

A hydraulic system (1) includes: a variable-capacity type steering pump (21) which supplies working oil to a steering actuator (11); a variable-capacity type cargo pump (31) which supplies working oil to at least one cargo actuator (12); and a confluence line (71) which branches off from a steering supply line (22) and is connected to a cargo supply line (32). The hydraulic system (1) further includes: a cargo regulator (5) which receives input of a cargo demand command pressure and in which the capacity of the cargo pump (31) increases as the cargo demand command pressure increases; and a steering regulator (4) for receiving, as a load sensing pressure, input of one of a steering load pressure or a cargo load pressure that is higher than the other and for controlling the capacity of the steering pump (21) such that the differential pressure between the load sensing pressure and the discharge pressure of the steering pump (21) becomes constant.

Description

Industrial vehicle hydraulic system

This disclosure relates to hydraulic systems for industrial vehicles.

Industrial vehicles such as wheel loaders and forklifts are equipped with a hydraulic system that includes a steering circuit for changing the direction of travel and a cargo handling circuit for moving the bucket and forks.

For example, Patent Document 1 discloses a hydraulic system for a forklift in which a variable displacement steering pump is used in the steering circuit and a variable displacement cargo handling pump is used in the cargo handling circuit. In the steering circuit, hydraulic fluid is supplied from the steering pump to the steering actuator via the steering supply line and steering valve, and in the cargo handling circuit, the cargo handling pump supplies the cargo handling supply line and two cargo handling control valves to the two cargo handling actuators. oil is supplied.

Furthermore, in the hydraulic system disclosed in Patent Document 1, a merging line branches off from the steering supply line, and this merging line is connected to the cargo handling supply line. A switching valve is provided in the merging line. The switching valve shuts off the merging line when a cargo handling operation is not performed, and opens the merging line when a cargo handling operation is performed. That is, when the merging line is released by the switching valve, the hydraulic oil discharged from the steering pump is combined with the hydraulic oil discharged from the cargo handling pump and supplied to the cargo handling actuator. When the cargo handling operation is performed simultaneously with the steering operation, hydraulic fluid discharged from the steering pump is supplied to both the steering actuator and the cargo handling actuator.

　The displacement of the steering pump is changed by the steering regulator, and the capacity of the cargo handling pump is changed by the cargo handling regulator. From the viewpoint of joining the hydraulic fluid discharged from the steering pump to the hydraulic fluid discharged from the cargo handling pump as described above, the displacement of the steering pump and the displacement of the cargo handling pump are controlled in the same manner. In Patent Document 1, load sensing control is adopted as the control method.

More specifically, the maximum load pressure, which is the higher of the load pressures of the two cargo handling actuators, is input to the cargo handling regulator as the load sensing pressure. The cargo handling regulator controls the displacement of the cargo handling pump so that the differential pressure between the load sensing pressure and the discharge pressure of the cargo handling pump is constant.

On the other hand, the higher of the load pressure of the steering actuator and the maximum load pressure of the cargo handling actuator is input to the steering regulator as the load sensing pressure. The steering regulator controls the displacement of the steering pump so that the differential pressure between the load sensing pressure and the discharge pressure of the steering pump is constant. Therefore, when steering operation and cargo handling operation are performed at the same time, the displacement of the steering pump changes according to the higher demand.

JP 2017-226492 A

By the way, as a control method for the capacity of the cargo handling pump, instead of load sensing control, there is a demand to adopt positive control that increases the capacity as the amount of cargo handling operation increases. However, in this case, the problem is how to control the displacement of the steering pump.

Therefore, an object of the present disclosure is to provide a hydraulic system for an industrial vehicle that can control the displacement of a cargo handling pump by positive control and appropriately control the displacement of a steering pump.

The present disclosure provides a variable displacement steering pump that supplies hydraulic fluid to a steering actuator via a steering supply line and a steering valve, and hydraulic fluid to at least one cargo handling actuator via a cargo handling supply line and at least one cargo handling control valve. a variable displacement cargo handling pump that supplies the cargo handling supply line, a junction line branched from the steering supply line and connected to the cargo handling supply line, and a junction line provided in the junction line that shuts off the junction line when no cargo handling operation is performed. Then, a priority valve for opening the merging line when a cargo handling operation is performed, and a cargo handling request command pressure that indicates a positive correlation with the operation amount of the cargo handling operation are input. a steering load pressure that is the pressure downstream of a throttle that determines the amount of hydraulic fluid supplied to the steering actuator in the steering valve; and the at least one cargo handling in the cargo handling supply line. The higher one of the cargo handling load pressures, which are the pressures on the upstream side of the control valve, is input as the load sensing pressure, and the pressure difference between the load sensing pressure and the discharge pressure of the steering pump is kept constant. and a steering regulator for controlling displacement.

According to the present disclosure, the displacement of the cargo handling pump can be positively controlled, and the displacement of the steering pump can be appropriately controlled.

1 is a schematic configuration diagram of a hydraulic system of an industrial vehicle according to one embodiment; FIG. 4 is an enlarged view of a steering circuit of the hydraulic system; FIG. 4 is an enlarged view of a cargo handling circuit of the hydraulic system; FIG. It is an operation system circuit diagram of the said cargo-handling circuit.

FIG. 1 shows a hydraulic system 1 for an industrial vehicle according to one embodiment. In this embodiment, the industrial vehicle is a wheel loader that includes a hoist (also called an arm or boom) and a bucket. However, the industrial vehicle may be a forklift or the like.

The hydraulic system 1 includes a steering circuit 2 for changing the direction of travel and a cargo handling circuit 3 for moving the bucket. In a wheel loader, a front vehicle body including front wheels and a rear vehicle body including rear wheels are connected so as to be able to swing horizontally. A hoist is connected to the front vehicle body so as to be able to swing in the vertical direction, and a bucket is connected to the tip of the hoist so as to be able to swing in the vertical direction.

The steering circuit 2 includes a steering pump 21, a steering valve 23 and a steering actuator 11, as shown in FIG. The steering pump 21 supplies hydraulic fluid to the steering actuator 11 via a steering supply line 22 and a steering valve 23 . In this embodiment, the steering actuator 11 is composed of a pair of hydraulic cylinders provided on both left and right sides of the connecting portion between the front vehicle body and the rear vehicle body. However, depending on the size of the wheel loader, the steering actuator 11 may be composed of a single hydraulic cylinder. If the industrial vehicle is a forklift, the steering actuator 11 is composed of a single double-rod hydraulic cylinder.

Specifically, the steering pump 21 is connected to the steering valve 23 by a steering supply line 22, and the steering valve 23 is connected to the steering actuator 11 by a pair of supply/discharge lines 24. Also, the steering valve 23 is connected to the tank by a tank line 25 .

The steering valve 23 has a throttle portion 23 a that determines the amount of hydraulic oil supplied to the steering actuator 11 . Both ends of an intermediate line 27 interposed between the steering supply line 22 and the supply/discharge line 24 are also connected to the steering valve 23 . A check valve 28 is provided in the intermediate line 27 .

The steering valve 23 shifts from the neutral position to the right turning position or the left turning position when a handle provided in the driver's cab of the industrial vehicle is operated. In the neutral position, the steering supply line 22, both ends of the intermediate line 27, the pair of supply/discharge lines 24 and the tank line 25 are all blocked. At the right turning position or the left turning position, the steering supply line 22 communicates with one supply/discharge line 24 via the intermediate line 27 , and the other supply/discharge line 24 communicates with the tank line 25 . At the right turn position or the left turn position, the opening area of the throttle portion 23a increases as the amount of operation of the handle increases.

More specifically, the steering valve 23 has a pair of pilot ports, and these pilot ports are connected to the Orbitroll (registered trademark) 26 by

pilot lines

26a and 26b. The orbit roll 26 is connected to the steering wheel, and outputs a pilot pressure corresponding to the amount of operation of the steering wheel to the pilot port of the steering valve 23 through a

pilot line

26a or 26b in the rotating direction of the steering wheel.

Furthermore, a load pressure line 64 and a tank line 68 are also connected to the steering valve 23 . The load pressure line 64 communicates with the tank line 68 when the steering valve 23 is in the neutral position. When the steering valve 23 is positioned at the right-turning position or the left-turning position, the steering load pressure, which is the pressure on the downstream side of the throttle portion 23a, is introduced to the load pressure line 64 .

A compensator 61 is provided in the steering supply line 22 . The compensator 61 opens the steering supply line 22 at the neutral position, and the opening area of the compensator 61 decreases as the compensator 61 shifts from the neutral position. The pressure on the upstream side of the throttle portion 23a of the steering valve 23 and the above-described steering load pressure act on the compensator 61 so as to oppose each other.

The steering load pressure is guided to the compensator 61 through the load pressure line 64 described above, and acts on the compensator 61 so as to shift in the direction of increasing the opening area. On the other hand, the pressure on the upstream side of the throttle portion 23a in the steering valve 23 is guided to the compensator 61 through the supply pressure line 62, and acts on the compensator 61 so as to shift the opening area in the direction of decreasing. The supply pressure line 62 branches off from the steering supply line 22 downstream of the compensator 61 . In this embodiment, the supply pressure line 62 and the load pressure line 64 are provided with the

throttles

63 and 65, respectively, but the

throttles

63 and 65 can be omitted.

With such a configuration, the opening area of the compensator 61 decreases as the differential pressure between the pressure on the upstream side of the throttle portion 23a of the steering valve 23 and the steering load pressure increases. A relief line 66 branches from the load pressure line 64, and a relief valve 67 provided in the relief line 66 keeps the pressure of the load pressure line 64 below a predetermined value.

The steering pump 21 described above is driven by the prime mover. The prime mover is, for example, an internal combustion engine or an electric motor. The prime mover also drives a cargo handling pump 31 and a sub-pump 15, which will be described later.

The steering pump 21 is a variable displacement pump. In this embodiment, the steering pump 21 is a swash plate pump having a swash plate 21a. However, the steering pump 21 may be a tilted shaft pump. In this embodiment, the relief line 17 branches off from a portion of the confluence line 71 on the upstream side of the priority valve 72, which will be described later. kept below. The relief line 17 may branch off from the steering supply line 22 .

The displacement of the steering pump 21 is changed by the steering regulator 4. A load sensing pressure is input to the steering regulator 4 through a load sensing line 99 . The steering regulator 4 controls the displacement of the steering pump 21 so that the differential pressure between the load sensing pressure and the discharge pressure of the steering pump 21 is constant. In this embodiment, the steering regulator 4 is configured as shown in FIG. 2, but the configuration of the steering regulator 4 is not limited to this and can be changed as appropriate.

More specifically, the steering regulator 4 includes a spring 41 that biases the swash plate 21a in the capacity increasing direction, and a piston 42 that presses the swash plate 21a against the spring 41 in the capacity decreasing direction. A pressure receiving chamber 43 for applying control pressure to the piston 42 is formed in the steering regulator 4 .

Furthermore, the steering regulator 4 includes a load sensing valve 45 connected to the pressure receiving chamber 43 by a control pressure line 44 and a cutoff valve 48 provided on the control pressure line 44 . However, the cutoff valve 48 can be omitted.

The load sensing valve 45 is connected to the steering supply line 22 by a pump pressure line 46 and is connected to the tank by a tank line 47 . Further, the load sensing pressure and the discharge pressure of the steering pump 21 act on the load sensing valve 45 so as to oppose each other. The load sensing valve 45 operates so that the differential pressure between the load sensing pressure and the discharge pressure of the steering pump 21 is constant, and the control pressure thus adjusted is introduced into the pressure receiving chamber 43 through the control pressure line 44. .

The cut-off valve 48 introduces the discharge pressure of the steering pump 21 into the pressure receiving chamber 43 to minimize the displacement of the steering pump 21 when the discharge pressure of the steering pump 21 exceeds a set value.

The cargo handling circuit 3 includes a cargo handling pump 31, two cargo handling control valves 33, and two cargo handling actuators 12, as shown in FIG. The cargo handling pump 31 supplies hydraulic oil to the two cargo handling actuators 12 via the cargo handling supply line 32 and the two cargo handling control valves 33 .

The two cargo handling actuators 12 are the bucket actuator 13 and the hoist actuator 14 . In this embodiment, the bucket actuator 13 is composed of a single hydraulic cylinder, and the hoist actuator 14 is composed of a pair of hydraulic cylinders. However, the bucket actuator 13 may be composed of a pair of hydraulic cylinders. The two cargo control valves 33 are a bucket control valve 34 and a hoist control valve 35 .

Specifically, the cargo handling pump 31 is connected to the bucket control valve 34 and the hoist control valve 35 by the cargo handling supply line 32 . That is, the cargo handling supply line 32 includes a common passage 32 a extending from the cargo handling pump 31 , a bucket branch passage 32 b extending from the downstream end of the common passage 32 a to the bucket control valve 34 , and extending from the downstream end of the common passage 32 a to the hoist control valve 35 . Includes hoist branch 32c. The bucket branch passage 32b and the hoist branch passage 32c are provided with

check valves

32d and 32e, respectively.

Further, the hoist branch passage 32c is provided with a bucket priority valve 32f for limiting the supply of hydraulic oil to the hoist actuator 14 when the bucket operation and the hoist operation are performed simultaneously. The bucket priority valve 32f opens the hoist branch passage 32c at the neutral position, and the opening area of the bucket priority valve 32f decreases as the bucket priority valve 32f shifts from the neutral position. In this embodiment, the bucket priority valve 32f is of a pilot type and has a pilot port. As the pilot pressure introduced to the pilot port of the bucket priority valve 32f increases, the opening area of the bucket priority valve 32f decreases. However, the bucket priority valve 32f may be of an electromagnetic type.

The bucket control valve 34 described above is connected to the bucket actuator 13 by a pair of supply/discharge lines 36 , and the hoist control valve 35 is connected to the hoist actuator 14 by a pair of supply/discharge lines 37 . Also, the bucket control valve 34 and the hoist control valve 35 are connected to the tank by a tank line 38 .

The bucket control valve 34 shifts from the neutral position to the first operating position or the second operating position. In the neutral position, the cargo handling supply line 32, the pair of supply and discharge lines 36 and the tank line 38 are all blocked. In the first operating position or the second operating position, the cargo handling supply line 32 communicates with one supply/discharge line 36 , and the other supply/discharge line 36 communicates with the tank line 38 .

In this embodiment, the bucket control valve 34 is of a pilot type and has a pair of pilot ports. When the pilot pressure is introduced into one of the pilot ports, the bucket control valve 34 shifts from the neutral position to the first operating position, and the opening area of the bucket control valve 34 increases as the pilot pressure increases. Conversely, when pilot pressure is introduced to the other pilot port, bucket control valve 34 shifts from the neutral position to the second operating position, and the opening area of bucket control valve 34 increases as the pilot pressure increases. However, the bucket control valve 34 may be of an electromagnetic type.

The hoist control valve 35 shifts from the neutral position to the first operating position or the second operating position. Additionally, the hoist control valve 35 also shifts between the second and third operating positions. In the neutral position, the cargo handling supply line 32, the pair of supply and discharge lines 37 and the tank line 38 are all blocked. At the first operating position or the second operating position, the cargo handling supply line 32 communicates with one supply/discharge line 37 , and the other supply/discharge line 37 communicates with the tank line 38 . In the third operating position, the supply and discharge lines 37 communicate with each other within the hoist control valve 35 .

　In this embodiment, the hoist control valve 35 is of a pilot type and has a pair of pilot ports. When pilot pressure is introduced into one of the pilot ports, the hoist control valve 35 shifts from the neutral position to the first operating position, and the opening area of the hoist control valve 35 increases as the pilot pressure increases. Conversely, when pilot pressure is introduced into the other pilot port, the hoist control valve 35 shifts from the neutral position to the second operating position, and the opening area of the hoist control valve 35 increases as the pilot pressure increases. As the pilot pressure introduced to the other pilot port further increases, the hoist control valve 35 shifts from the second operating position to the third operating position. However, the hoist control valve 35 may be electromagnetic.

Furthermore, in this embodiment, a center bypass line 39 branches off from the common path 32a of the cargo handling supply line 32, and this center bypass line 39 passes through the bucket control valve 34 and the hoist control valve 35 and extends to the tank. . The bucket control valve 34 and the hoist control valve 35 decrease the opening area on the center bypass line 39 as they shift from the neutral position to the first operating position or the second operating position.

As shown in FIG. 4, the pilot port of the bucket control valve 34 is connected via a pair of pilot lines to a pair of proportional

bucket solenoid valves

94 and 95, and the pilot port of the hoist control valve 35 is connected via a pair of pilot lines to a pair of

proportional bucket valves

94 and 95. hoist electromagnetic

proportional valves

96 and 97. The bucket electromagnetic

proportional valves

94, 95 and the hoist electromagnetic

proportional valves

96, 97 are connected by the primary pressure line 16 to the auxiliary pump 15 (see FIGS. 1 and 3). Although not shown, a relief line branches off from the primary pressure line 16, and the discharge pressure of the auxiliary pump 15 is maintained at a predetermined value by a relief valve provided in this relief line. The primary pressure line 16 may be connected to the steering supply line 22 instead of the sub-pump 15, and a pressure reducing valve may be provided in the primary pressure line 16 to reduce the discharge pressure of the steering pump 21 and use it as the primary pressure.

In this embodiment, each of the bucket electromagnetic

proportional valves

94, 95 and the hoist electromagnetic

proportional valves

96, 97 is a direct proportional type in which the command current and the secondary pressure exhibit a positive correlation. However, each of the bucket electromagnetic

proportional valves

94, 95 and the hoist electromagnetic

proportional valves

96, 97 may be of the inverse proportional type in which the command current and the secondary pressure exhibit a negative correlation.

Returning to FIG. 3, the driver's cab of the industrial vehicle is provided with a bucket operating device 92 and a hoist operating device 93 in addition to the steering wheel described above. The bucket operation device 92 includes an operation lever for bucket operation, and the hoist operation device 93 includes an operation lever for hoist operation.

In this embodiment, each of the bucket operation device 92 and the hoist operation device 93 is an electric joystick that outputs an electric signal according to the tilting direction and tilting angle of the control lever (that is, the amount of bucket operation or hoist operation). . Electrical signals output from the bucket operation device 92 and the hoist operation device 93 are input to the control device 91 .

However, each of the bucket operation device 92 and the hoist operation device 93 may be a pilot operation valve that outputs a pilot pressure corresponding to the tilting direction and tilting angle of the operation lever. In this case, the bucket electromagnetic

proportional valves

94, 95 and the hoist electromagnetic

proportional valves

96, 97 are omitted, and the pilot port of the bucket control valve 34 is connected by a pair of pilot lines to the bucket operation device 92, which is a pilot operation valve. A pilot port of the hoist control valve 35 may be connected to a hoist operating device 93, which is a pilot operated valve, via a pair of pilot lines.

When the operation lever of the bucket operation device 92 receives a bucket operation, the control device 91 supplies a command current to the bucket electromagnetic

proportional valve

94 or 95 corresponding to the tilting direction of the operation lever. Further, the control device 91 increases the command current as the operation amount of the bucket operation increases. The secondary pressure output from one of the bucket solenoid proportional valves 94 (the one that swings the bucket upward) is also guided to the pilot port of the above-described bucket priority valve 32f as shown in FIG.

Similarly, when the operation lever of the hoist operation device 93 receives a hoist operation, the control device 91 sends a command current to the hoist electromagnetic

proportional valve

96 or 97 corresponding to the tilting direction of the operation lever. Further, the control device 91 increases the command current as the operation amount of the hoist operation increases.

With respect to the controller 91, the functions of the elements disclosed herein can be general purpose processors, special purpose processors, integrated circuits, Application Specific Integrated Circuits (ASICs), conventional circuits, configured or programmed to perform the functions disclosed. and/or combinations thereof. A processor is considered a processing circuit or circuit because it includes transistors and other circuits. In this disclosure, a circuit, unit, or means is hardware that performs or is programmed to perform the recited functions. The hardware may be the hardware disclosed herein, or other known hardware programmed or configured to perform the recited functions. A circuit, means or unit is a combination of hardware and software where the hardware is a processor which is considered a type of circuit, the software being used to configure the hardware and/or the processor.

The cargo handling pump 31 described above is a variable displacement pump. In this embodiment, the cargo handling pump 31 is a swash plate pump having a swash plate 31a. However, the cargo handling pump 31 may be a bent shaft pump. A relief line 18 branches from the cargo handling supply line 32, and a relief valve 18a provided in the relief line 18 keeps the discharge pressure of the cargo handling pump 31 at a predetermined value or less. When a priority valve 72, which will be described later, is opened, the relief valve 18a also serves to keep the discharge pressure of the steering pump 21 below a predetermined value.

The capacity of the cargo handling pump 31 is changed by the cargo handling regulator 5 . In this embodiment, the cargo handling regulator 5 performs flow control using the flow control piston 56 and horsepower control using the horsepower control piston 57 . However, the cargo handling regulator 5 may perform only flow rate control.

A cargo handling request command pressure is input to the cargo handling regulator 5 for flow rate control. The cargo handling request command pressure will be described later in detail. The cargo handling regulator 5 increases the displacement of the cargo handling pump 31 as the required cargo handling command pressure increases. In this embodiment, the cargo handling regulator 5 is configured as shown in FIG. 3, but the configuration of the cargo handling regulator 5 is not limited to this, and can be changed as appropriate.

More specifically, the cargo handling regulator 5 includes a servo piston 51 connected to the swash plate 31a of the cargo handling pump 31 and an adjustment valve 52 for driving the servo piston 51, in addition to the flow control piston 56 and the horsepower control piston 57. include. The cargo handling regulator 5 also includes a housing that slidably holds the flow control piston 56, the horsepower control piston 57, and the servo piston 51. As shown in FIG. Part of the housing may be integrated with the casing of the cargo pump 31 .

The cargo handling regulator 5 is formed with a first pressure receiving chamber 5a into which the discharge pressure of the cargo handling pump 31 is introduced and a second pressure receiving chamber 5b into which the control pressure is introduced. The servo piston 51 has a first end exposed in the first pressure receiving chamber 5a and a second end exposed in the second pressure receiving chamber 5b and having a larger diameter than the first end.

The adjustment valve 52 is for adjusting the control pressure introduced into the second pressure receiving chamber 5b. Specifically, the regulating valve 52 includes a spool 53 that moves in a direction of decreasing the control pressure (capacity increasing direction, leftward in FIG. 3) and a direction of increasing the control pressure (capacity decreasing direction, rightward in FIG. 3), and a spool It includes a sleeve 54 that accommodates 53 .

The spool 53 is connected to the flow rate control piston 56 via a lever 56a, and is connected to the horsepower control piston 57 via a lever 57a. The spool 53 moves in the capacity increasing direction as the flow control piston 56 moves forward, and moves in the capacity decreasing direction as the flow control piston 56 moves backward. Further, the spool 53 moves in the capacity decreasing direction as the horsepower control piston 57 advances, and moves in the capacity increasing direction as the flow rate control piston 56 moves backward. The flow rate control piston 56 and the horsepower control piston 57 are configured so that the one that restricts the capacity to a small value (that is, the one that commands a smaller capacity) preferentially moves the spool 53 .

The sleeve 54 is connected with the servo piston 51 by a feedback lever 55 . The sleeve 54 is formed with a pump port, a tank port, and an output port (the output port communicates with the second pressure receiving chamber 5b). port, or the output port is in communication with either the pump port or the tank port. When the spool 53 is moved in the capacity increasing direction or the capacity decreasing direction, the relative positions of the spool 53 and the sleeve 54 are determined so that the forces acting from both sides of the servo piston 51 (pressure×servo piston pressure receiving area) are balanced. , the control pressure is adjusted.

Further, the cargo handling regulator 5 is formed with an operation chamber 5c for applying the cargo handling request command pressure to the flow rate control piston 56 . In other words, the flow rate control piston 56 advances when the required cargo handling command pressure increases, and moves backward when the required cargo handling command pressure decreases.

Further, the cargo handling regulator 5 is formed with an operating chamber 5 d for applying the discharge pressure of the cargo handling pump 31 to the horsepower control piston 57 . That is, the horsepower control piston 57 moves forward when the discharge pressure of the cargo handling pump 31 increases, and moves backward when the discharge pressure decreases.

In this embodiment, the working chamber 5c is connected to the electromagnetic proportional valve 81 through the command pressure line 82. The electromagnetic proportional valve 81 is connected to the sub-pump 15 (the steering supply line 22 in the case of the modified example described above) through the primary pressure line 16 described above. In this embodiment, the proportional solenoid valve 81 is of a direct proportional type in which the command current and the secondary pressure exhibit a positive correlation. However, the electromagnetic proportional valve 81 may be of an inverse proportional type in which the command current and the secondary pressure exhibit a negative correlation.

The electromagnetic proportional valve 81 is controlled by the control device 91 described above, and outputs the secondary pressure to the working chamber 5c as the cargo handling request command pressure. The control device 91 sends a command current to the electromagnetic proportional valve 81 when a cargo handling operation (bucket operation or hoist operation) is performed. In addition, the control device 91 increases the command current as the operation amount of the cargo handling operation increases. That is, the cargo handling request command pressure exhibits a positive correlation with the manipulated variable of the cargo handling operation.

Next, the load sensing pressure input to the steering regulator 4 will be explained. The load sensing line 99 described above is connected to the output port of the high pressure selection valve 98, as shown in FIG. One of the pair of input ports of the high pressure selection valve 98 is connected to the load pressure line 64 by an input line 88, and the other is connected to the cargo handling/supply line 32 by an input line 89 (see FIG. 3).

The high pressure selection valve 98 selects the higher one of the cargo handling load pressure, which is the pressure on the upstream side of the cargo handling control valve 33 in the cargo handling supply line 32 and the steering load pressure, and outputs it to the steering regulator 4 . In other words, the higher one of the cargo handling load pressure and the steering request command pressure is input to the steering regulator 4 as the aforementioned load sensing pressure.

As shown in FIGS. 1 to 3, a junction line 71 branches off from the steering supply line 22 upstream of the compensator 61, and the junction line 71 is connected to the cargo handling supply line 32. A priority valve 72 is provided in the merge line 71 .

The priority valve 72 shuts off the merging line 71 when cargo handling operations are not performed, and opens the merging line 71 when cargo handling operations are performed. In this embodiment, the priority valve 72 is piloted and has a first pilot port 72a and a second pilot port 72b. However, the priority valve 72 may be of an electromagnetic type.

More specifically, the priority valve 72 blocks the confluence line 71 at the neutral position, and the opening area of the priority valve 72 increases as the priority valve 72 shifts from the neutral position. The priority valve 72 has a spring 72c (see FIG. 2) for maintaining the priority valve 72 in a neutral position. The first pilot port 72a is connected to the tank by a pilot line 73. As shown in FIG. The pilot line 73 is provided with a check valve 74 and is connected to a bypass line 75 that bypasses the check valve 74 . A throttle 76 is provided in the bypass line 75 . The second pilot port 72b is for shifting the priority valve 72 in the direction of increasing the opening area.

That is, when the priority valve 72 shifts from the neutral position, the throttle 76 restricts the outflow of hydraulic oil from the first pilot port 72a, so the priority valve 72 operates slowly. Conversely, when the priority valve 72 returns to the neutral position, hydraulic fluid smoothly flows into the first pilot port 72a via the check valve 74, so the priority valve 72 operates quickly. The check valve 74, bypass line 75 and throttle 76 can be omitted.

A second pilot port 72 b of the priority valve 72 is connected to the switching valve 84 by a pilot line 77 . The switching valve 84 is connected to the command pressure line 82 by a pilot line 83 and is connected to the tank by a tank line 85 . Note that the pilot line 83 may be connected to the working chamber 5 c of the cargo handling regulator 5 instead of the command pressure line 82 .

The switching valve 84 switches whether or not to output the cargo handling request command pressure, which is the secondary pressure of the electromagnetic proportional valve 81 , to the second pilot port 72 b of the priority valve 72 . In this embodiment, the switching valve 84 is of a pilot type and has a first pilot port 84a and a second pilot port 84b. However, the switching valve 84 may be of an electromagnetic type.

More specifically, the switching valve 84 shifts between a neutral position in which the pilot line 77 communicates with the tank line 85 and an operating position in which the pilot line 77 communicates with the pilot line 83 . The switching valve 84 has a spring 84c for maintaining the switching valve 84 in a neutral position. The first pilot port 84a is located on the same side as the spring 84c and the second pilot port 84b is located on the opposite side of the spring 84c.

The first pilot port 84 a is connected to the load pressure line 64 by a pilot line 86 . That is, the steering load pressure is introduced to the first pilot port 84a. In this embodiment, a portion of the pilot line 86 and a portion of the input line 88 described above form a common flow path. The second pilot port 84 b is connected to the cargo handling/supply line 32 by a pilot line 87 . That is, cargo handling load pressure is introduced to the second pilot port 84b. In this embodiment, a portion of the pilot line 87 and a portion of the input line 89 described above form a common flow path.

When the cargo handling load pressure is smaller than the reference pressure obtained by adding a predetermined value (pressure corresponding to the biasing force of the spring 84c) to the steering load pressure, the switching valve 84 is positioned at the neutral position to set the cargo handling request command pressure to the second pilot. No output to port 84b. On the other hand, when the cargo handling request command pressure is higher than the reference pressure, the switching valve 84 shifts to the operating position to output the cargo handling request command pressure to the second pilot port 84b.

As described above, in the hydraulic system 1 of the present embodiment, the cargo handling demand command pressure that exhibits a positive correlation with the operation amount of the cargo handling operation is input to the cargo handling regulator 5, so the displacement of the cargo handling pump 31 is controlled by positive control. can do. On the other hand, the higher one of the steering load pressure and the cargo handling load pressure is input to the steering regulator 4 as the load sensing pressure. When the steering operation is performed alone, the steering load pressure is input to the steering regulator 4, so the displacement of the steering pump 21 changes according to the steering load pressure. Further, when the cargo handling operation is performed alone, the cargo handling load pressure is input to the steering regulator 4, so that the displacement of the steering pump 21 changes according to the cargo handling load pressure. Hydraulic oil is supplied to the cargo handling actuator 12 . When the steering operation and the cargo handling operation are performed simultaneously, the displacement of the steering pump 21 changes according to the higher demand. Therefore, the displacement of the steering pump 21 can be appropriately controlled.

Furthermore, in this embodiment, the priority valve 72 provided in the merging line 71 is of a pilot type, so the priority valve 72 can be mechanically operated. Moreover, since the load-handling request command pressure output to the second pilot port 82b of the priority valve 72 has a positive correlation with the amount of load-handling operation, the opening area of the priority valve 72 increases as the load-handling operation amount decreases. becomes smaller. Therefore, the hydraulic oil discharged from the steering pump 21 can be preferentially supplied to the steering actuator 11 .

(Modification)
The present disclosure is not limited to the embodiments described above, and various modifications are possible without departing from the gist of the present disclosure.

For example, depending on the type of industrial vehicle, the number of cargo handling actuators 12 and the number of cargo handling control valves 33 in the cargo handling circuit 3 of the hydraulic system 1 may be one, or three or more.

Further, when each of the bucket operation device 92 and the hoist operation device 93 is a pilot operation valve, the electromagnetic proportional valve 81 may be omitted, and the pilot pressure output from the bucket operation device 92 and the pilot pressure output from the hoist operation device 93 may be omitted. The highest pilot pressure among the pressures may be guided to the working chamber 5c of the cargo handling regulator 5 as the cargo handling demand command pressure.

Also, the switching valve 84 does not necessarily have to be an on-off valve, and may have a function of a pressure reducing valve capable of reducing the cargo handling operation request command pressure.

(summary)
The present disclosure provides a variable displacement steering pump that supplies hydraulic fluid to a steering actuator via a steering supply line and a steering valve, and hydraulic fluid to at least one cargo handling actuator via a cargo handling supply line and at least one cargo handling control valve. a variable displacement cargo handling pump that supplies the cargo handling supply line, a junction line branched from the steering supply line and connected to the cargo handling supply line, and a junction line provided in the junction line that shuts off the junction line when no cargo handling operation is performed. Then, a priority valve for opening the merging line when a cargo handling operation is performed, and a cargo handling request command pressure that indicates a positive correlation with the operation amount of the cargo handling operation are input. a steering load pressure that is the pressure downstream of a throttle that determines the amount of hydraulic fluid supplied to the steering actuator in the steering valve; and the at least one cargo handling in the cargo handling supply line. The higher one of the cargo handling load pressures, which are the pressures on the upstream side of the control valve, is input as the load sensing pressure, and the pressure difference between the load sensing pressure and the discharge pressure of the steering pump is kept constant. and a steering regulator for controlling displacement.

According to the above configuration, the cargo handling demand command pressure that exhibits a positive correlation with the operation amount of the cargo handling operation is input to the cargo handling regulator, so the capacity of the cargo handling pump can be controlled by positive control. On the other hand, the higher one of the steering load pressure and the cargo handling load pressure is input to the steering regulator as the load sensing pressure. When the steering operation is performed alone, the steering load pressure is input to the steering regulator, so the displacement of the steering pump changes according to the steering load pressure. Also, when the cargo handling operation is performed independently, the cargo handling load pressure is input to the steering regulator, so the displacement of the steering pump changes according to the cargo handling load pressure. oil is supplied. When steering operation and cargo handling operation are performed at the same time, the displacement of the steering pump changes according to the higher demand. Therefore, the displacement of the steering pump can be appropriately controlled.

For example, the above hydraulic system may further include a high pressure selection valve that selects the higher one of the steering load pressure and the cargo handling load pressure and outputs it to the steering regulator.

The priority valve blocks the merging line at a neutral position, and has a pilot port that shifts the priority valve in a direction in which the opening area increases. A switching valve for switching whether or not to output to a pilot port, wherein when the cargo handling load pressure is smaller than a reference pressure obtained by adding a predetermined value to the steering load pressure, the cargo handling request command pressure is not output and the cargo handling demand command pressure is not output. A switching valve may be further provided for outputting the cargo handling request command pressure when the load pressure is higher than the reference pressure. According to this configuration, the priority valve can be mechanically operated. Moreover, the demand command pressure for cargo handling output to the pilot port of the priority valve shows a positive correlation with the amount of cargo handling operation. can be preferentially supplied to the steering actuator.

Reference Signs List 1 hydraulic system 11 steering actuator 12 cargo handling actuator 2 steering circuit 21 steering pump 22 steering supply line 23 steering valve 23a throttle section 3 cargo handling circuit 31 cargo handling pump 32 cargo handling supply line 33 cargo handling control valve 4 steering regulator 5 cargo handling regulator 71 merging line 72 priority Valve 72a First pilot port 72b Second pilot port 84 Switching valve 98 High pressure selection valve

Claims

a variable displacement steering pump that supplies hydraulic fluid to a steering actuator via a steering supply line and a steering valve;
a variable displacement cargo handling pump that supplies hydraulic oil to at least one cargo handling actuator via a cargo handling supply line and at least one cargo handling control valve;
a confluence line branched from the steering supply line and connected to the cargo handling supply line;
a priority valve provided in the merging line for blocking the merging line when a cargo handling operation is not performed and opening the merging line when a cargo handling operation is performed;
a cargo handling regulator to which a cargo handling command pressure that is positively correlated with the manipulated variable of the cargo handling operation is input, and that increases the capacity of the cargo handling pump as the cargo handling command pressure increases;
A steering load pressure, which is a downstream pressure of a throttle portion that determines the amount of hydraulic oil supplied to the steering actuator in the steering valve, and a pressure upstream of the at least one cargo handling control valve in the cargo handling supply line. a steering regulator that receives the higher one of the cargo handling load pressures as a load sensing pressure and controls the displacement of the steering pump so that the differential pressure between the load sensing pressure and the discharge pressure of the steering pump is constant;
A hydraulic system of an industrial vehicle, comprising:
The hydraulic system for an industrial vehicle according to claim 1, further comprising a high-pressure selection valve that selects the higher one of the steering load pressure and the cargo handling load pressure and outputs it to the steering regulator.
The priority valve blocks the merging line at a neutral position, and has a pilot port that shifts the priority valve in a direction in which the opening area increases,
A switching valve for switching whether or not to output the cargo-handling request command pressure to the pilot port, wherein when the cargo-handling load pressure is smaller than a reference pressure obtained by adding a predetermined value to the steering load pressure, the cargo-handling request command pressure is output. 3. The hydraulic system for an industrial vehicle according to claim 1, further comprising a switching valve that does not output the cargo handling load pressure and outputs the cargo handling request command pressure when the cargo handling load pressure is greater than the reference pressure.