A spreader control hydraulic circuit, a reachstacker hydraulic control system and a reachstacker

Abstract

The invention discloses a spreader control hydraulic circuit, a reachstacker hydraulic control system and a reachstacker, belonging to the technical field of reachstackers. The spreader control hydraulic circuit includes a leveling cylinder, a leveling valve group and an oil supply port P1; the leveling valve group includes a first leveling valve, a second leveling valve and a reversing control valve; when the first leveling valve and the second leveling valve are simultaneously conducted, the spreader performs adaptive leveling under the action of gravity; the reversing control valve is provided with a first conduction mode and a second conduction mode; by switching the first conduction mode and the second conduction mode through the reversing control valve, the tilting direction of the spreader is switched. The invention can enable the spreader to perform adaptive leveling and switch the tilting direction of the spreader, reducing the lifting difficulty.

Description

Technical Field

[0001] The present invention relates to a spreader control hydraulic circuit, a reachstacker hydraulic control system and a reachstacker, belonging to the technical field of reachstackers. Background Art

[0002] With the booming development of the container industry, reachstackers are more and more widely used in container operations due to their characteristics of being flexible, occupying less space, having a high stacking layer, and being suitable for cross-container operations. They are especially suitable for the loading and unloading of containers at small and medium-sized ports, railway transfer stations and highway transfer stations, and can also be used as auxiliary equipment at large container terminals.

[0003] The spreader of the reachstacker is adjusted according to the size of the container and can be rotated to pass through narrow channels. For easy container alignment, the spreader can be laterally shifted left and right, and a leveling cylinder is installed on the spreader. The leveling cylinder makes the spreader have a certain inclination angle, so that the operator can align the container smoothly. During the movement, the leveling cylinder also has a leveling effect on the swing of the spreader.

[0004] The existing technology has the following disadvantages in controlling the leveling cylinder: the inclination angle α of the spreader is not controlled, which affects the operation efficiency. As Figure 1 shown, when the reachstacker is hoisting, from the movement trajectory of the spreader, it can be seen that as the boom luffing angle β changes, the force arm L of the leveling cylinder changes. Therefore, in order to keep the inclination angle of the spreader, the thrust of the leveling cylinder must change accordingly. However, in the existing technical solutions, since the pressure reducing valve is fixed, the pressure input to the cylinder is also fixed, and the generated thrust is constant. Therefore, as the boom luffing angle β changes, the inclination angle α of the spreader will also change. When α changes to a very small value, it will interfere with the operator's container alignment operation and affect the operation efficiency. Summary of the Invention

[0005] The purpose of the present invention is to overcome the deficiencies in the prior art and provide a spreader control hydraulic circuit, a reachstacker hydraulic control system and a reachstacker, which can make the spreader perform adaptive leveling, perform forward inclination control and backward inclination control on the spreader, and reduce the hoisting difficulty. To achieve the above purpose, the present invention is implemented by the following technical solutions:

[0006] In a first aspect, the present invention provides a spreader control hydraulic circuit, including a leveling cylinder, a leveling valve group and an oil supply port P1;

[0007] The leveling valve group includes a first leveling valve, a second leveling valve and a reversing control valve;

[0008] The first leveling valve is used to connect the oil supply port P1 and the large chamber oil port of the leveling cylinder, and the second leveling valve is used to connect the oil supply port P1 and the small chamber oil port of the leveling cylinder; when the first leveling valve and the second leveling valve are both opened, the pressure in the large chamber of the leveling cylinder is equal to the pressure in the small chamber, and the spreader is in the floating position, and the spreader performs adaptive leveling under the action of gravity.

[0009] The reversing control valve has a first conduction mode and a second conduction mode; in the first conduction mode, the oil supply port P1 is communicated with the large chamber oil port of the leveling cylinder, and in the second conduction mode, the oil supply port P1 is communicated with the small chamber oil port of the leveling cylinder; by switching the first conduction mode and the second conduction mode through the reversing control valve, the tilting direction of the spreader is switched.

[0010] Optionally, in combination with the first aspect, the spreader control hydraulic circuit further includes a return port T.

[0011] The inlet of the first leveling valve is connected to the oil supply port P1, and the outlet is connected to the large chamber oil port of the leveling cylinder. When the electromagnet of the first leveling valve is energized, the oil supply port P1 is communicated with the large chamber of the leveling cylinder, and the hydraulic oil flows from the large chamber through the small chamber and then enters the return port T.

[0012] The inlet of the second leveling valve is connected to the oil supply port P1, and the outlet is connected to the small chamber oil port of the leveling cylinder. When the electromagnet of the second leveling valve is energized, the oil supply port P1 is communicated with the small chamber of the leveling cylinder, and the hydraulic oil flows from the small chamber through the large chamber and then enters the return port T.

[0013] Wherein, the electromagnets of the first leveling valve and the second leveling valve are energized simultaneously, the large and small chambers of the leveling cylinder are communicated, and the spreader performs adaptive leveling vertically downward under the action of gravity.

[0014] Optionally, in combination with the first aspect, the spreader control hydraulic circuit further includes a return port T, the reversing control valve includes a first electromagnet and a second electromagnet, the tilting direction of the spreader includes a first direction and a second direction, and the first direction and the second direction are opposite directions.

[0015] When the first electromagnet is energized, it is the first conduction mode. The oil supply port P1 is connected to the small chamber oil port of the leveling cylinder through the reversing control valve. The hydraulic oil flows from the small chamber of the leveling cylinder through the large chamber and then enters the return port T. The piston rod of the leveling cylinder extends, and the spreader tilts in the first direction.

[0016] When the second electromagnet is energized, it is the second conduction mode. The oil supply port P1 is connected to the large chamber oil port of the leveling cylinder through the reversing control valve. The hydraulic oil flows from the large chamber of the leveling cylinder through the small chamber and then enters the return port T. The piston rod of the leveling cylinder retracts, and the spreader tilts in the second direction.

[0017] In combination with the first aspect, optionally, the spreader control hydraulic circuit further includes an oil drain port D and a pressure reducing valve with overflow function;

[0018] The inlet of the pressure reducing valve with overflow function is connected to the oil supply port P1, the outlet of the pressure reducing valve with overflow function is connected to the inlets of the first leveling valve and the second leveling valve, and the overflow port of the pressure reducing valve with overflow function is connected to the oil drain port D on the leveling valve body.

[0019] In combination with the first aspect, optionally, the spreader control hydraulic circuit further includes a damping regulating valve group for damping regulation of the spreader tilt, and the damping regulating valve group includes a throttle orifice with a large diameter and a throttle orifice with a small diameter;

[0020] The inlet of the damping regulating valve group is connected to the oil supply port P1, and the hydraulic oil is connected to the large chamber oil port of the leveling cylinder through the throttle orifice with a large diameter, and the hydraulic oil is connected to the small chamber oil port of the leveling cylinder through the throttle orifice with a small diameter.

[0021] In the second aspect, the present invention provides a reachstacker hydraulic control system, including: a hydraulic pump and the spreader control hydraulic circuit described in the first aspect, and the outlet of the hydraulic pump is connected to the oil supply port P1 of the spreader control hydraulic circuit.

[0022] In combination with the second aspect, optionally, it further includes a boom working hydraulic circuit, and the boom working hydraulic circuit includes a multi-way valve, an actuating cylinder and an oil supply port P2, and the actuating cylinder includes a telescopic cylinder and a luffing cylinder; the oil supply port P2 is connected to the outlet of the hydraulic pump;

[0023] When the multi-way valve connects the oil path between the oil supply port P2 and the telescopic cylinder, the piston rod of the telescopic cylinder extends or retracts to control the telescopic operation of the boom;

[0024] When the multi-way valve connects the oil path between the oil supply port P2 and the luffing cylinder, the piston rod of the luffing cylinder extends or retracts to control the luffing operation of the boom.

[0025] In combination with the second aspect, optionally, the multi-way valve includes a telescopic cylinder solenoid valve, a telescopic cylinder pilot reversing valve, a luffing cylinder solenoid valve and a luffing cylinder pilot reversing valve, and the reachstacker hydraulic control system further includes a pilot valve group;

[0026] The inlet of the pilot valve group is connected to the outlet of the hydraulic pump, and the outlet of the pilot valve group is connected to the telescopic cylinder pilot reversing valve and the luffing cylinder pilot reversing valve; the telescopic cylinder pilot reversing valve is used to push the spool of the telescopic cylinder solenoid valve to switch the passage; the luffing cylinder pilot reversing valve is used to push the spool of the luffing cylinder solenoid valve to switch the passage.

[0027] In combination with the second aspect, optionally, a logic valve is further included. The logic valve is used to compare the oil pressures of the first input oil circuit and the second input oil circuit, determine the input oil circuit with the higher oil pressure among the first input oil circuit and the second input oil circuit, and output the pressure signal of the oil pressure of the input oil circuit with the higher oil pressure to the hydraulic pump. The hydraulic pump adjusts the pressure of the output hydraulic oil according to the pressure signal;

[0028] A pressure reducing valve and a filter are provided in the pilot valve group. The high-pressure oil output by the hydraulic pump is reduced in pressure by the pressure reducing valve and then converted into low-pressure oil. The low-pressure oil is filtered by the filter and then input into the telescopic cylinder pilot reversing valve and the luffing cylinder pilot reversing valve. The low-pressure oil flowing out of the telescopic cylinder pilot reversing valve is input into the telescopic cylinder solenoid valve, and the low-pressure oil flowing out of the luffing cylinder pilot reversing valve is input into the luffing cylinder solenoid valve;

[0029] The first input oil circuit is the oil circuit output by the telescopic cylinder, and the second input oil circuit is the oil circuit output by the luffing cylinder.

[0030] In a third aspect, the present invention provides a reach stacker, and the reach stacker is configured with the reach stacker hydraulic control system described in the second aspect.

[0031] Compared with the prior art, the beneficial effects achieved by a spreader control hydraulic circuit, a reach stacker hydraulic control system, and a reach stacker provided by the embodiments of the present invention include:

[0032] The present invention provides a spreader control hydraulic circuit, including a leveling cylinder, a leveling valve group, and an oil supply port P1; the leveling valve group includes a first leveling valve, a second leveling valve, and a reversing control valve; the first leveling valve is used to connect the oil supply port P1 to the large chamber oil port of the leveling cylinder, and the second leveling valve is used to connect the oil supply port P1 to the small chamber oil port of the leveling cylinder; when the first leveling valve and the second leveling valve are simultaneously conducted, the pressure in the large chamber of the leveling cylinder is equal to the pressure in the small chamber, and the spreader is in the floating position, and the spreader performs adaptive leveling under the action of gravity; the present invention can enable the spreader to perform adaptive leveling when the reach stacker performs the boom raising action or the boom lowering action;

[0033] The reversing control valve of the present invention is provided with a first conduction mode and a second conduction mode; in the first conduction mode, the oil supply port P1 is communicated with the large chamber oil port of the leveling cylinder, and in the second conduction mode, the oil supply port P1 is communicated with the small chamber oil port of the leveling cylinder; by switching the first conduction mode and the second conduction mode through the reversing control valve, the tilting direction of the spreader is switched; the present invention can switch the tilting direction of the spreader according to the operator's personal operation habits or the ground conditions, and the operator can operate to switch the tilting direction of the spreader to meet the working conditions when the ground has an angle, which is convenient for accurate container handling;

[0034] The present invention enables the spreader to perform adaptive leveling and switch the tilting direction of the spreader, reducing the lifting difficulty and improving the work efficiency. Description of the Drawings

[0035] Figure 1 It is a schematic diagram of the tilting angle α of the spreader in the background art of the present invention;

[0036] Figure 2 It is a schematic diagram of a spreader control hydraulic circuit in Embodiment 1 of the present invention;

[0037] Figure 3 It is a schematic diagram of a reachstacker hydraulic control system in Embodiment 2 of the present invention.

[0038] In the figure:

[0039] 1, leveling valve group; 102, check valve; 103, relief valve; 104, relief reducing valve; 105, first leveling valve; 1051, electromagnet of the first leveling valve; 106, second leveling valve; 1061, electromagnet of the second leveling valve; 107, damping regulating valve group; 108, reversing control valve; 1081, first electromagnet of the reversing control valve; 1082, second electromagnet of the reversing control valve;

[0040] 2, left leveling cylinder;

[0041] 3, right leveling cylinder;

[0042] 4, hydraulic pump;

[0043] 5, pilot valve group; 501, reducing valve; 502, first filter; 503, accumulator;

[0044] 6, multi-way valve; 601, solenoid valve for telescopic cylinder; 602, solenoid valve for luffing cylinder; 603, pilot reversing valve for telescopic cylinder; 6031, first electromagnet of the pilot reversing valve for telescopic cylinder; 6032, second electromagnet of the pilot reversing valve for telescopic cylinder; 604, pilot reversing valve for luffing cylinder; 6041, first electromagnet of the pilot reversing valve for luffing cylinder; 6042, second electromagnet of the pilot reversing valve for luffing cylinder; 605, overload oil compensating valve; 606, LS unloading valve;

[0045] 7, telescopic cylinder;

[0046] 8, left luffing cylinder;

[0047] 9, right luffing cylinder;

[0048] 10, radiator;

[0049] 11, second filter;

[0050] 12, logic valve;

[0051] 13. Lifting appliance valve;

[0052] 14. Boom;

[0053] 15. Lifting appliance. Specific implementation mode

[0054] The technical solution of the present invention will be described in detail below with reference to the accompanying drawings and specific embodiments. It should be understood that the embodiments of the present invention and the specific features in the embodiments are detailed descriptions of the technical solution of the present invention, rather than limitations on the technical solution of the present invention. Without conflict, the technical features in the embodiments of the present invention and the embodiments can be combined with each other.

[0055] Embodiment 1

[0056] As Figure 2 shown, this embodiment provides a hydraulic circuit for controlling a lifting appliance, including: a leveling oil cylinder, a leveling valve group 1, and an oil supply port P1.

[0057] As Figure 2 shown, in this embodiment, the leveling oil cylinder includes a left leveling oil cylinder 2 and a right leveling oil cylinder 3 respectively arranged on both sides in the front-back direction of the lifting appliance. The large chambers and the small chambers of the left leveling oil cylinder and the right leveling oil cylinder are respectively communicated with each other to be able to extend or retract simultaneously, so as to provide sufficient torque for the forward or backward tilt of the lifting appliance.

[0058] Taking one end of the leveling oil cylinder being installed at the rear of the lifting appliance 15 as an example, this embodiment describes the relationship between the telescopic movement of the leveling oil cylinder and the tilting direction of the lifting appliance.

[0059] As Figure 1 shown, one end of the leveling oil cylinder is connected to the boom 14, and the other end is connected to the rear of the lifting appliance 15. Figure 1 The lifting appliance is in a forward tilt state, and in this state, the piston rod of the leveling oil cylinder is in an extended state.

[0060] As Figure 2 shown, the leveling valve group includes a reversing control valve, and a first leveling valve 105 and a second leveling valve 106 that can be simultaneously conducted. It also includes 1 overflow pressure reducing valve 104, 1 overflow valve 103, 1 set of damping regulating valve groups 107, and multiple one-way valves 102.

[0061] In Figure 2 order to facilitate the display, the corresponding oil inlet ports of the left leveling oil cylinder and the right leveling oil cylinder are named after the pressure measuring ports of the oil cylinder, including the oil port C-left connecting the large chamber oil port of the left leveling oil cylinder, the oil port C+left connecting the small chamber oil port of the left leveling oil cylinder, the oil port C-right connecting the large chamber oil port of the right leveling oil cylinder, and the oil port C+right connecting the large chamber oil port of the right leveling oil cylinder.

[0062] In this embodiment, the oil supply port P1 is connected to a hydraulic pump, the oil drain port D is connected to an oil drain tank for storing the drained oil, and the oil return port T is connected to a hydraulic oil tank for storing hydraulic oil. The hydraulic pump pumps the hydraulic oil in the hydraulic oil tank into the oil supply port P.

[0063] The first leveling valve is used to connect the oil supply port P1 to the large chamber oil port of the leveling cylinder, and the second leveling valve is used to connect the oil supply port P1 to the small chamber oil port of the leveling cylinder. When the first leveling valve and the second leveling valve are both opened, the pressure in the large chamber of the leveling cylinder is equal to the pressure in the small chamber, and the spreader is in the floating position, and the spreader performs adaptive leveling under the action of gravity.

[0064] The inlet of the first leveling valve is connected to the oil supply port P1, and the outlet is connected to the large chamber oil port of the leveling cylinder. When the electromagnet 1051 of the first leveling valve is energized, the oil supply port P1 is communicated with the large chamber of the leveling cylinder, and the hydraulic oil flows from the large chamber through the small chamber and then enters the return port T.

[0065] The inlet of the second leveling valve is connected to the oil supply port P1, and the outlet is connected to the small chamber oil port of the leveling cylinder. When the electromagnet 1052 of the second leveling valve is energized, the oil supply port P1 is communicated with the small chamber of the leveling cylinder, and the hydraulic oil flows from the small chamber through the large chamber and then enters the return port T.

[0066] The electromagnet 1051 of the first leveling valve and the electromagnet 1052 of the second leveling valve are energized simultaneously, the large and small chambers of the leveling cylinder are communicated, and the spreader performs adaptive leveling vertically downward under the action of gravity.

[0067] In this embodiment, as Figure 2 shown, the connection of the oil supply port P1 to the large chamber of the leveling cylinder means that the oil supply port P1 is connected to the large chambers of the left leveling cylinder and the right leveling cylinder.

[0068] In this embodiment, as Figure 2 shown, the connection of the oil supply port P1 to the small chamber of the leveling cylinder means that the oil supply port P1 is connected to the small chambers of the left leveling cylinder and the right leveling cylinder.

[0069] In this embodiment, as Figure 2 shown, both the first leveling valve and the second leveling valve are two-position two-way electromagnetic directional control valves.

[0070] The reversing control valve has a first conduction mode and a second conduction mode. In the first conduction mode, the oil supply port P1 is communicated with the large chamber oil port of the leveling cylinder, and in the second conduction mode, the oil supply port P1 is communicated with the small chamber oil port of the leveling cylinder. By switching the first conduction mode and the second conduction mode of the reversing control valve, the tilting direction of the spreader is switched. The tilting direction of the spreader includes a first direction and a second direction, and the first direction and the second direction are opposite directions.

[0071] As Figure 2As shown, the direction-changing control valve includes the first electromagnet 1081 of the direction-changing control valve and the second electromagnet 1082 of the direction-changing control valve.

[0072] When the first electromagnet 1081 of the direction-changing control valve is energized, it is in the first conduction mode. The oil supply port P1 is connected to the small chamber oil port of the leveling cylinder through the direction-changing control valve. The hydraulic oil flows from the small chamber of the leveling cylinder through the large chamber and then enters the return port T. The piston rod of the leveling cylinder extends, and the spreader tilts in the first direction.

[0073] In this embodiment, the first direction is the front. Refer to Figure 1 , when the piston rod of the leveling cylinder extends, the spreader tilts forward.

[0074] When the second electromagnet 1082 of the direction-changing control valve is energized, it is in the second conduction mode. The oil supply port P1 is connected to the large chamber oil port of the leveling cylinder through the direction-changing control valve. The hydraulic oil flows from the large chamber of the leveling cylinder through the small chamber and then enters the return port T. The piston rod of the leveling cylinder retracts, and the spreader tilts in the second direction.

[0075] In this embodiment, the second direction is the rear. By analogy with Figure 1 , when the piston rod of the leveling cylinder retracts, the spreader tilts backward.

[0076] In this embodiment, as Figure 2 shown, the direction-changing control valve is a three-position four-way electromagnetic direction-changing valve.

[0077] This embodiment enables the operator to actively tilt the spreader forward or backward according to personal operating habits or ground conditions to meet the working conditions when the ground has an angle, facilitating accurate container alignment operations.

[0078] The inlet of the overflow pressure reducing valve is connected to the oil supply port P1. The outlet of the overflow pressure reducing valve is connected to the inlets of the first leveling valve and the second leveling valve. The overflow port of the overflow pressure reducing valve is connected to the drain port D on the leveling valve body.

[0079] In this embodiment, the overflow pressure reducing valve is an overflow pressure reducing valve with adjustable pressure.

[0080] As Figure 2 shown, a check valve is provided between the overflow port and the drain port D of the overflow pressure reducing valve to prevent the oil overflowing from the drain cylinder from interfering with the overflow pressure reducing valve.

[0081] The inlet of the damping regulating valve group is connected to the oil supply port P1, and the outlet is connected to the oil ports C-left, C+left, C-right, and C+right.

[0082] The damping regulating valve group is used to damp the forward and backward tilting of the spreader. The damping regulating valve group can slow down the forward and backward tilting actions.

[0083] Specifically, the damping regulating valve group includes a throttle orifice with a large aperture and a throttle orifice with a small aperture.

[0084] The outlet of the throttle orifice with a large aperture is connected to oil ports C-left and C-right. The hydraulic oil is connected to the large chamber oil port of the leveling cylinder through the throttle orifice with a large aperture. A check valve is connected in parallel with the throttle orifice with a large aperture, and the allowed flow direction is from the outlet of the throttle orifice with a large aperture to the inlet direction, which is used to ensure that the hydraulic oil flows through the throttle orifice with a large aperture.

[0085] The outlet of the throttle orifice with a small aperture is connected to oil ports C+left and C+right. The hydraulic oil is connected to the desired chamber oil port of the leveling cylinder through the throttle orifice with a small aperture. A check valve is connected in parallel with the throttle orifice with a small aperture, and the allowed flow direction is from the outlet of the throttle orifice with a small aperture to the inlet direction, which is used to ensure that the hydraulic oil flows through the throttle orifice with a small aperture.

[0086] In this embodiment, as Figure 2 shown, a pressure measuring port MP- is provided on the leveling valve body, which is used to measure the pressure in the large chambers of the left and right leveling cylinders. A pressure measuring port MP+ is provided on the leveling valve body, which is used to measure the pressure in the small chambers of the left and right leveling cylinders.

[0087] The spreader control hydraulic circuit provided in this embodiment can enable the spreader to perform adaptive leveling, front tilt control and rear tilt control on the spreader, reduce the lifting difficulty and improve the work efficiency.

[0088] Embodiment 2

[0089] As Figure 3 shown, this embodiment provides a reachstacker hydraulic control system, which includes: a hydraulic pump 4 and a spreader control hydraulic circuit provided in Embodiment 1. The outlet of the hydraulic pump is connected to the oil supply port P1 of the spreader control hydraulic circuit.

[0090] In this embodiment, a reachstacker hydraulic control system is configured with an oil drain tank for storing drained oil and a hydraulic oil tank for storing hydraulic oil. The oil drain tank is connected to the oil drain port D of the spreader control hydraulic circuit, and the hydraulic oil tank is connected to the oil return port T of the spreader control hydraulic circuit. The hydraulic pump pumps the hydraulic oil in the hydraulic oil tank into the oil supply port P1.

[0091] A reachstacker hydraulic control system further includes a boom working hydraulic circuit.

[0092] The boom working hydraulic circuit includes a pilot valve group 5, a multi-way valve 6, an actuator cylinder and an oil supply port P2. The oil supply port P2 is connected to the outlet of the hydraulic pump.

[0093] As Figure 3 shown, the actuator cylinder includes a telescopic cylinder 7 and a luffing cylinder.

[0094] When the multi-way valve connects the oil circuit between the oil supply port P2 and the telescopic cylinder, the piston rod of the telescopic cylinder extends or retracts to control the telescopic movement of the boom.

[0095] When the multi-way valve connects the oil circuit between the oil supply port P2 and the luffing cylinder, the piston rod of the luffing cylinder extends or retracts to control the luffing movement of the boom.

[0096] In this embodiment, the luffing cylinder includes a left luffing cylinder 8 and a right luffing cylinder 9, and the two luffing cylinders perform the same operation simultaneously. The two luffing cylinders are provided to meet the flow rate required for the luffing operation and to improve the balance on both sides of the spreader during adjustment.

[0097] The multi-way valve includes an oil drain port D, an oil return port T, a pilot control oil port Ps, a feedback control oil port Ls, and oil ports A1 and A1' for connecting to the large chamber of the telescopic cylinder, oil ports B1 and B1' for connecting to the small chamber of the telescopic cylinder, an oil port A2 for connecting to the large chamber of the left luffing cylinder, an oil port B2 for connecting to the small chamber of the left luffing cylinder, an oil port A2' for connecting to the large chamber of the right luffing cylinder, and an oil port B2' for connecting to the small chamber of the left luffing cylinder.

[0098] The multi-way valve includes a telescopic cylinder solenoid valve 601, a telescopic cylinder pilot reversing valve 603, a luffing cylinder solenoid valve 602, and a luffing cylinder pilot reversing valve 604. The telescopic cylinder pilot reversing valve is used to push the spool of the telescopic cylinder solenoid valve to switch the passage. The luffing cylinder pilot reversing valve is used to push the spool of the luffing cylinder solenoid valve to switch the passage.

[0099] In this embodiment, both the telescopic cylinder solenoid valve and the luffing cylinder solenoid valve are three-position seven-way solenoid valves. The telescopic cylinder pilot reversing valve includes a first electromagnet 6031 and a second electromagnet 6032 of the telescopic cylinder pilot reversing valve, and the luffing cylinder pilot reversing valve includes a first electromagnet 6041 and a second electromagnet 6042 of the luffing cylinder pilot reversing valve.

[0100] When the first electromagnet 6031 of the telescopic cylinder pilot reversing valve is energized and the second electromagnet 6032 is not energized, Figure 3 the spool of the telescopic cylinder solenoid valve moves downward, the oil ports B1 and B1' of the oil supply port P2 and the small chamber of the telescopic cylinder are connected, the oil supply port P2 is connected to the small chamber of the telescopic cylinder, the hydraulic oil flows from the small chamber into the large chamber, the piston rod of the telescopic cylinder extends, and the hydraulic oil enters the return port T through the telescopic cylinder solenoid valve.

[0101] When the first electromagnet 6031 of the telescopic cylinder pilot reversing valve is not energized and the second electromagnet 6032 is energized, Figure 3When the spool of the solenoid valve of the telescopic oil cylinder moves upward, the oil supply port P2 is connected to the oil ports A1 and A1' of the large chamber of the telescopic oil cylinder. The oil supply port P2 is connected to the large chamber of the telescopic oil cylinder. The hydraulic oil flows from the large chamber into the large chamber, the piston rod of the telescopic oil cylinder retracts, and the hydraulic oil enters the return port T through the solenoid valve of the telescopic oil cylinder.

[0102] When the first electromagnet 6041 of the pilot directional control valve of the luffing oil cylinder is energized and the second electromagnet 6042 of the pilot directional control valve of the luffing oil cylinder is not energized, Figure 3 When the spool of the solenoid valve of the luffing oil cylinder moves downward, the oil supply port P2 is connected to the oil ports B2 and B2' of the small chamber of the luffing oil cylinder. The oil supply port P2 is connected to the small chamber of the luffing oil cylinder. The hydraulic oil flows from the small chamber into the large chamber, the piston rod of the luffing oil cylinder extends, and the hydraulic oil enters the return port T through the solenoid valve of the luffing oil cylinder.

[0103] When the first electromagnet 6041 of the pilot directional control valve of the luffing oil cylinder is not energized and the second electromagnet 6042 of the pilot directional control valve of the luffing oil cylinder is energized, Figure 3 When the spool of the solenoid valve of the luffing oil cylinder moves upward, the oil supply port P2 is connected to the oil ports A2 and A2' of the large chamber of the luffing oil cylinder. The oil supply port P2 is connected to the large chamber of the luffing oil cylinder. The hydraulic oil flows from the large chamber into the large chamber, the piston rod of the luffing oil cylinder retracts, and the hydraulic oil enters the return port T through the solenoid valve of the luffing oil cylinder.

[0104] The multi-way valve further includes an overload oil replenishing valve 605 and an LS unloading valve 606. The overload oil replenishing valve is used to prevent the oil cylinder from being overloaded, prevent the suction hole when the oil cylinder starts quickly, and replenish oil to the oil cylinder. The LS unloading valve is used to discharge the excess LS oil into the return port T when the oil cylinder does not perform actions.

[0105] In this embodiment, a radiator 10 for cooling the hydraulic oil and a second filter 11 for ensuring the cleanliness of the hydraulic oil are arranged between the return port T of the multi-way valve and the hydraulic oil tank.

[0106] The hydraulic control system of the reach stacker further includes a pilot valve group 5. The inlet of the pilot valve group is connected to the outlet of the hydraulic pump, and the outlet of the pilot valve group is connected to the pilot directional control valve of the telescopic oil cylinder and the pilot directional control valve of the luffing oil cylinder. The pilot valve group is used to process the hydraulic oil and then input it into the control oil circuit of the multi-way valve.

[0107] Specifically, a pressure reducing valve 501 and a first filter 502 are provided in the pilot valve group. The high-pressure oil output by the hydraulic pump is reduced in pressure by the pressure reducing valve and then converted into the low-pressure oil required by the control oil circuit. The low-pressure oil is filtered by the filter and then input into the pilot directional control valve of the telescopic oil cylinder and the pilot directional control valve of the luffing oil cylinder from the pilot control oil port Ps. The low-pressure oil flowing out of the pilot directional control valve of the telescopic oil cylinder is input into the solenoid valve of the telescopic oil cylinder, and the low-pressure oil flowing out of the pilot directional control valve of the luffing oil cylinder is input into the solenoid valve of the luffing oil cylinder.

[0108] The boom working hydraulic circuit further includes a logic valve 12. The logic valve is used to compare the oil pressures of the first input oil circuit and the second input oil circuit, determine the input oil circuit with the higher oil pressure among the first input oil circuit and the second input oil circuit, and output the pressure signal of the oil pressure of the input oil circuit with the higher oil pressure to the hydraulic pump. The hydraulic pump adjusts the pressure of the output hydraulic oil according to the pressure signal.

[0109] Specifically, the logic valve outputs the pressure signal from the feedback control oil port Ls to the hydraulic pump, and the low-pressure oil discharged by the logic valve enters the return port T.

[0110] Among them, the first input oil circuit is the oil circuit output by the telescopic cylinder, and the second input oil circuit is the oil circuit output by the luffing cylinder.

[0111] In this embodiment, an accumulator 503 and a relief valve are further provided in the pilot valve group after the pressure reducing valve. The accumulator is used to store hydraulic oil for the control oil circuit. In this embodiment, the relief valve is a 40-bar relief valve, which is used to overflow the excess hydraulic oil when the pressure of the accumulator reaches 40 bar.

[0112] As Figure 3 shown, a spreader valve 13 is also provided in this embodiment. The spreader valve includes a pressure reducing and overflow valve, a relief valve and a directional control valve. When the spreader control hydraulic circuit performs adaptive leveling control, spreader forward tilt control or spreader rearward tilt control, the electromagnet of the directional control valve is energized, and the pressure signal is output from the feedback control oil port Ls to the hydraulic pump. The hydraulic pump outputs hydraulic oil to the oil supply port P of the leveling valve body. The pressure reducing and overflow valve is used to reduce the high-pressure hydraulic oil output by the hydraulic pump to the pressure required by the leveling cylinder. The relief valve is used to prevent the leveling cylinder from being overloaded.

[0113] In this embodiment, as Figure 3 shown, the hydraulic pump is two parallel hydraulic pumps. The hydraulic pump is a variable pump.

[0114] As Figure 3 shown, a hydraulic pump controller is connected to the hydraulic pump. The hydraulic pump controller is used to adjust the pressure of the hydraulic oil output by the hydraulic pump according to the pressure signal output from the feedback control oil port Ls. A check valve group is provided at the outlet of the hydraulic pump to prevent the hydraulic oil from flowing back.

[0115] Furthermore, a reachstacker hydraulic control system is further configured with a spreader operating cylinder connected to the spreader. This configuration is similar to the existing setting and will not be specifically described in this embodiment.

[0116] This embodiment is described in combination with a spreader control hydraulic circuit provided in Embodiment 1 to enable the spreader to perform adaptive leveling when the reachstacker performs the boom raising action or the boom lowering action.

[0117] When the boom of the reachstacker is lifted, the hydraulic pump supplies oil, the pilot directional control valve of the luffing cylinder is activated, pushing the spool of the luffing cylinder solenoid valve. After the hydraulic oil is regulated for oil supply through the multi-way valve, it enters the small chamber of the luffing cylinder. The piston rod of the luffing cylinder extends, lifting the boom of the reachstacker and raising the spreader. At this time, the controller detects that the multi-way valve is energized, and simultaneously energizes the first leveling valve and the second leveling valve in the spreader control hydraulic circuit. The large and small chambers of the leveling cylinder are connected, and the spreader is in the floating position, vertically downward under the action of gravity, realizing the adaptive leveling control of the spreader during the boom lifting operation.

[0118] When the boom of the reachstacker is lowered, the hydraulic pump supplies oil, the pilot directional control valve of the luffing cylinder is activated, pushing the spool of the luffing cylinder solenoid valve. After the hydraulic oil is regulated for oil supply through the multi-way valve, it enters the large chamber of the luffing cylinder. The piston rod of the luffing cylinder retracts, the boom of the reachstacker drops, and the spreader drops. At this time, the controller detects that the multi-way valve is energized, and simultaneously energizes the first leveling valve and the second leveling valve in the spreader control hydraulic circuit. The large and small chambers of the leveling cylinder are connected, and the spreader is in the floating position, vertically downward under the action of gravity, realizing the adaptive leveling control of the spreader during the boom lowering operation.

[0119] Embodiment 3

[0120] This embodiment provides a reachstacker, which is configured with the reachstacker hydraulic control system described in Embodiment 2.

[0121] The embodiments of the present invention have been described above in conjunction with the accompanying drawings. However, the present invention is not limited to the above specific embodiments. The above specific embodiments are merely illustrative and not restrictive. Under the inspiration of the present invention, those of ordinary skill in the art can also make many forms without departing from the spirit and scope protected by the claims of the present invention. These all fall within the protection scope of the present invention.

Claims

1. A hydraulic control system for a reach stacker, characterized in that: It includes a hydraulic pump and a spreader control hydraulic circuit, wherein the outlet of the hydraulic pump is connected to the oil supply port P1 of the spreader control hydraulic circuit; and also includes a boom working hydraulic circuit; The sling control hydraulic circuit includes a leveling cylinder, a leveling valve group and an oil supply port P1; The leveling valve group includes a first leveling valve, a second leveling valve and a reversing control valve; The first leveling valve is used to connect the oil supply port P1 with the large chamber oil port of the leveling oil cylinder, and the second leveling valve is used to connect the oil supply port P1 with the small chamber oil port of the leveling oil cylinder; when the first leveling valve and the second leveling valve are turned on at the same time, the pressure of the large chamber of the leveling oil cylinder is equal to the pressure of the small chamber, the spreader is in a floating position, and the spreader is adaptively leveled under the action of gravity; The spreader control hydraulic circuit also includes a return port T; The inlet of the first leveling valve is connected to the oil supply port P1, and the outlet is connected to the large chamber oil port of the leveling cylinder. When the electromagnet of the first leveling valve is energized, the oil supply port P1 is connected to the large chamber of the leveling cylinder, and the hydraulic oil flows from the large chamber through the small chamber and enters the return port T; The inlet of the second leveling valve is connected to the oil supply port P1, and the outlet is connected to the small chamber oil port of the leveling cylinder. When the electromagnet of the second leveling valve is energized, the oil supply port P1 is connected to the small chamber of the leveling cylinder, and the hydraulic oil flows from the small chamber through the large chamber and then enters the return port T; The electromagnet of the first leveling valve and the electromagnet of the second leveling valve are energized at the same time, the large and small chambers of the leveling oil cylinder are connected, and the sling is adaptively leveled vertically downward under the action of gravity; The reversing control valve is provided with a first conduction mode and a second conduction mode; in the first conduction mode, the oil supply port P1 is connected with the large chamber oil port of the leveling oil cylinder, and in the second conduction mode, the oil supply port P1 is connected with the small chamber oil port of the leveling oil cylinder; the inclination direction of the spreader is switched by switching the first conduction mode and the second conduction mode through the reversing control valve; The boom working hydraulic circuit includes a multi-way valve, an actuator cylinder and an oil supply port P2, wherein the actuator cylinder includes a telescopic cylinder and a luffing cylinder; the oil supply port P2 is connected to the outlet of the hydraulic pump; When the multi-way valve connects the oil circuit between the oil supply port P2 and the telescopic cylinder, the piston rod of the telescopic cylinder extends or retracts to control the telescopic operation of the boom; When the multi-way valve connects the oil circuit between the oil supply port P2 and the luffing cylinder, the piston rod of the luffing cylinder extends or retracts to control the luffing operation of the boom; The multi-way valve includes a telescopic cylinder solenoid valve, a telescopic cylinder pilot reversing valve, a luffing cylinder solenoid valve and a luffing cylinder pilot reversing valve, and the front crane hydraulic control system also includes a pilot valve group; The inlet of the pilot valve group is connected to the outlet of the hydraulic pump, and the outlet of the pilot valve group is connected to the telescopic cylinder pilot reversing valve and the boom cylinder pilot reversing valve; the telescopic cylinder pilot reversing valve is used to push the valve core of the telescopic cylinder solenoid valve to switch the passage; the boom cylinder pilot reversing valve is used to push the valve core of the boom cylinder solenoid valve to switch the passage.

2. The hydraulic control system of the reach stacker according to claim 1, characterized in that: The spreader control hydraulic circuit further includes a return port T, the reversing control valve includes a first electromagnet and a second electromagnet, the spreader tilting direction includes a first direction and a second direction, and the first direction and the second direction are opposite directions; When the first electromagnet is energized, it is in the first conduction mode, the oil supply port P1 is connected to the small chamber oil port of the leveling cylinder through the reversing control valve, the hydraulic oil flows from the small chamber of the leveling cylinder through the large chamber and then enters the return port T, the piston rod of the leveling cylinder extends, and the sling is tilted in the first direction; When the second electromagnet is energized, it is in the second conduction mode, the oil supply port P1 is connected to the large chamber oil port of the leveling cylinder through the reversing control valve, the hydraulic oil flows from the large chamber of the leveling cylinder through the small chamber and then enters the return port T, the piston rod of the leveling cylinder retracts, and the sling tilts in the second direction.

3. The hydraulic control system of the reach stacker according to claim 1, characterized in that: The sling control hydraulic circuit also includes an oil drain port D and a relief pressure reducing valve; The inlet of the relief pressure reducing valve is connected to the oil supply port P1, the outlet of the relief pressure reducing valve is connected to the inlet of the first leveling valve and the inlet of the second leveling valve, and the overflow port of the relief pressure reducing valve is connected to the oil drain port D on the valve body of the leveling valve.

4. The hydraulic control system of the reach stacker according to claim 1, characterized in that: The spreader control hydraulic circuit also includes a damping regulating valve group for damping the spreader tilt, and the damping regulating valve group includes a large-aperture throttle hole and a small-aperture throttle hole; The inlet of the damping regulating valve group is connected to the oil supply port P1, the hydraulic oil is connected to the large-cavity oil port of the leveling cylinder through the large-diameter throttle hole, and the hydraulic oil is connected to the small-cavity oil port of the leveling cylinder through the small-diameter throttle hole.

5. The hydraulic control system of the reach stacker according to claim 1, characterized in that: It also includes a logic valve, the logic valve is used to compare the oil pressures of the first input oil circuit and the second input oil circuit, determine the input oil circuit with greater oil pressure between the first input oil circuit and the second input oil circuit, output a pressure signal of the oil pressure of the input oil circuit with greater oil pressure to the hydraulic pump, and the hydraulic pump adjusts the pressure of the output hydraulic oil according to the pressure signal; The pilot valve group is provided with a pressure reducing valve and a filter. The high-pressure oil output by the hydraulic pump is converted into low-pressure oil after being reduced in pressure by the pressure reducing valve. The low-pressure oil is filtered by the filter and then input into the telescopic cylinder pilot reversing valve and the luffing cylinder pilot reversing valve. The low-pressure oil flowing out of the telescopic cylinder pilot reversing valve is input into the telescopic cylinder solenoid valve, and the low-pressure oil flowing out of the luffing cylinder pilot reversing valve is input into the luffing cylinder solenoid valve. The first input oil circuit is the oil circuit output by the telescopic oil cylinder, and the second input oil circuit is the oil circuit output by the luffing oil cylinder.

6. A reach stacker, characterized in that: The reach stacker is equipped with the reach stacker hydraulic control system according to any one of claims 1-5.

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