A hydraulic system for container reach crane

Abstract

The present invention discloses a hydraulic system for a container front crane, comprising an oil source, an oil tank, a damping oil cylinder, a forward and backward tilting reversing valve, and also comprising a first electric proportional throttle valve, a second electric proportional throttle valve and a pressure relief valve. The rod chamber of the damping oil cylinder is connected to the rodless chamber of the damping oil cylinder through the first electric proportional throttle valve and the second electric proportional throttle valve connected in series, the oil inlet of the pressure relief valve is connected to the oil source, the oil outlet of the pressure relief valve is connected to the oil path between the first electric proportional throttle valve and the second electric proportional throttle valve, and the oil drain port of the pressure relief valve is connected to the oil tank. The speed of the front and rear tilting of the crane can be adjusted, the center of gravity of the container can be found before the container is transported, and the possibility of rollover can be greatly reduced by adjusting the center of gravity of the container to be close to the center axis of the vehicle. The front and rear swing speed of the crane can be adjusted during the container transportation process, so as to adapt to the transportation on bumpy and pothole roads, and can also operate stably in off-road environments, thereby improving the safety of the transportation process.

Description

Technical Field

[0001] The invention relates to the field of hydraulic systems, and in particular to a hydraulic system for a container reach crane. Background Art

[0002] Reach-lift container crane is also called reach-lift, which is a special equipment mainly used for container handling. The spreader is the working device of the reach-lift. Before handling, the spreader is aligned with the container, and then the container is locked to ensure that the container does not fall during the handling process. When the spreader arrives at the designated location, it is unlocked and the container is lowered.

[0003] Since reach stackers are mostly used in ports, railways and other places with flat roads, the lifting equipment of reach stackers is also designed based on this environment. Furthermore, in order to prevent rollover, the center of gravity of the whole vehicle will be designed on the left and right center lines of the vehicle, and the boom of the reach stacker will also be arranged along the left and right center axis.

[0004] However, in scenarios such as emergency rescue, farms, and military operations, the handling of containers involves many off-road scenarios. During transportation on bumpy roads, if the center of gravity of the container deviates from the left and right center lines of the vehicle by a large distance and the container is heavy, the reach loader is susceptible to a large lateral inertia force, causing the vehicle to overturn. It is difficult to make the road surface flat in outdoor yards, so the container set may be uneven from front to back and from left to right. It is difficult for traditional spreaders to ensure that the vehicle is always perpendicular to the container during the container alignment process, which seriously affects the operating efficiency. In off-road environments, it is very easy for the spreader to swing violently back and forth, affecting driving safety.

[0005] Therefore, how to provide a hydraulic system for a container reach stacker that can reduce lateral forces during transportation on bumpy roads is a technical problem that technicians in this field currently need to solve. Summary of the invention

[0006] The object of the present invention is to provide a hydraulic system for a container front crane sling, in which a damping cylinder cooperates with a first electric proportional throttle valve, a second electric proportional throttle valve and a pressure reducing relief valve to achieve adjustable speed of the sling's forward and backward tilting. During container handling, the sling's forward and backward swinging speed can be adjusted, thereby improving the safety of the handling process.

[0007] To solve the above technical problems, the present invention provides a hydraulic system for a container front crane sling, comprising an oil source, an oil tank, a damping oil cylinder and a forward and backward tilt reversing valve, one end of the damping oil cylinder is connected to a boom assembly, the other end of the damping oil cylinder is connected to a rotating assembly, an oil inlet and an oil return port of the forward and backward tilt reversing valve are respectively connected to the oil source and the oil tank, two working oil ports of the forward and backward tilt reversing valve are respectively connected to a rod chamber and a rodless chamber of the damping oil cylinder, and further comprises a first electric proportional throttle valve, a second electric proportional throttle valve and a pressure reducing relief valve, the rod chamber of the damping oil cylinder is connected to the rodless chamber of the damping oil cylinder through the first electric proportional throttle valve and the second electric proportional throttle valve connected in series, the oil inlet of the pressure reducing relief valve is connected to the oil source, the oil outlet of the pressure reducing relief valve is connected to the oil circuit between the first electric proportional throttle valve and the second electric proportional throttle valve, and the oil drain port of the pressure reducing relief valve is connected to the oil tank.

[0008] Preferably, it also includes a first safety valve and two one-way valves, the rod chamber and the rodless chamber of the damping cylinder are respectively connected to the inlets of the two one-way valves, and the outlets of the two one-way valves are connected to the oil tank through the first safety valve.

[0009] Preferably, it comprises two damping oil cylinders which are arranged in parallel and move synchronously, the rod chambers of the two damping oil cylinders are connected to each other, and the rodless chambers of the two damping oil cylinders are connected to each other.

[0010] Preferably, it includes a left tilt cylinder, a right tilt cylinder and a tilt reversing valve, one end of the left tilt cylinder and the right tilt cylinder are connected to the rotating assembly, and the other end is connected to the sling assembly, the oil inlet and oil return port of the tilt reversing valve are respectively connected to the oil source and the oil tank, one working oil port of the tilt reversing valve is simultaneously connected to the rod chamber of the left tilt cylinder and the rodless chamber of the right tilt cylinder, the other working oil port of the tilt reversing valve is simultaneously connected to the rodless chamber of the left tilt cylinder and the rod chamber of the right tilt cylinder, the two working oil ports of the tilt reversing valve are connected through a floating valve, and the floating valve can control the conduction state of the two working oil ports of the tilt reversing valve.

[0011] Preferably, a two-way speed regulating valve is also included, wherein one working oil port of the roll reversing valve is connected to another working oil port of the roll reversing valve through the floating valve and the two-way speed regulating valve connected in series, and the two-way speed regulating valve can maintain a constant two-way flow rate.

[0012] Preferably, it also includes an oil drain valve, one end of which is connected to a working oil port of the roll reversing valve, and the other end of which is connected to the oil tank.

[0013] Preferably, two balancing valves are respectively provided at the two working oil ports of the roll reversing valve.

[0014] Preferably, it comprises two left tilt cylinders and two right tilt cylinders which move synchronously, the rod chambers of the two left tilt cylinders and the rodless chambers of the two right tilt cylinders are connected to each other, and the rodless chambers of the two left tilt cylinders and the rod chambers of the two right tilt cylinders are connected to each other.

[0015] Preferably, it includes a side shift reversing valve, a rotary lock reversing valve and a telescopic reversing valve connected in parallel with each other, and the side shift reversing valve is connected to the side shift oil cylinder, the rotary lock reversing valve is connected to the rotary lock oil cylinder, the telescopic reversing valve is connected to the telescopic oil cylinder, the oil source is connected to the oil inlets of the side shift reversing valve, the rotary lock reversing valve and the telescopic reversing valve through an electric proportional speed control valve, and a second safety valve is provided at the outlet of the electric proportional speed control valve.

[0016] Preferably, it includes a motor reversing valve, a shuttle valve, a hydraulic motor and a brake connected in sequence, the two oil ports of the hydraulic motor are connected to a third safety valve and a fourth safety valve in parallel, the flow directions of the third safety valve and the fourth safety valve are opposite, and the return oil port of the motor reversing valve is provided with a back pressure valve.

[0017] The present invention provides a hydraulic system for a container front crane sling, comprising an oil source, an oil tank, a damping oil cylinder, and a forward and backward tilt reversing valve, wherein one end of the damping oil cylinder is connected to a boom assembly, and the other end of the damping oil cylinder is connected to a rotating assembly, an oil inlet and an oil return port of the forward and backward tilt reversing valve are respectively connected to the oil source and the oil tank, two working oil ports of the forward and backward tilt reversing valve are respectively connected to a rod chamber and a rodless chamber of the damping oil cylinder, and further comprises a first electric proportional throttle valve, a second electric proportional throttle valve and a pressure reducing relief valve, the rod chamber of the damping oil cylinder is connected to the rodless chamber of the damping oil cylinder through the first electric proportional throttle valve and the second electric proportional throttle valve connected in series, the oil inlet of the pressure reducing relief valve is connected to the oil source, the oil outlet of the pressure reducing relief valve is connected to the oil circuit between the first electric proportional throttle valve and the second electric proportional throttle valve, and the oil drain port of the pressure reducing relief valve is connected to the oil tank.

[0018] When the reach stacker is transporting containers, the spreader assembly will swing back and forth. If the swing speed of the spreader assembly is too fast, the corresponding electric proportional throttle valve can be adjusted to reduce the opening to reduce the swing speed of the spreader assembly. Compared with the traditional fixed damping method, the adjustable damping can adapt to complex and changeable vehicle usage scenarios, and the normal extension and contraction of the damping cylinder can be ensured by the pressure reducing relief valve, so that the speed of the spreader's forward and backward tilting can be adjusted. Before transporting the container, the center of gravity of the container can be found, and the possibility of rollover can be greatly reduced by adjusting the center of gravity of the container close to the center axis of the vehicle. During the container transportation process, the swing speed of the spreader can be adjusted to adapt to the transportation on bumpy and pothole-prone roads, and it can also operate stably in off-road environments, thereby improving the safety of the transportation process. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] FIG1 is a hydraulic principle diagram of a specific embodiment of a hydraulic system for a container reach stacker provided by the present invention;

[0020] FIG2 is a structural schematic diagram of a specific embodiment of the hydraulic system of a container reach stacker provided by the present invention;

[0021] FIG3 is a hydraulic principle diagram of a forward and backward tilting system of a specific embodiment of a hydraulic system for a container reach stacker provided by the present invention;

[0022] FIG4 is a hydraulic principle diagram of a tilting system in a specific embodiment of a hydraulic system for a container reach stacker provided by the present invention;

[0023] FIG5 is a hydraulic principle diagram of a displacement system in a specific embodiment of a hydraulic system for a container reach stacker provided by the present invention;

[0024] FIG. 6 is a hydraulic principle diagram of a motor system in a specific embodiment of the hydraulic system for a container reach stacker provided by the present invention.

[0025] Among them, oil source 1, oil tank 2, damping cylinder 3, front and rear tilt reversing valve 4, first electric proportional throttle valve 5, second electric proportional throttle valve 6, pressure reducing relief valve 7, first safety valve 8, one-way valve 9, left tilt cylinder 10, right tilt cylinder 11, tilt reversing valve 12, floating valve 13, two-way speed regulating valve 14, oil drain valve 15, balance valve 16, side shift reversing valve 17, rotary lock reversing valve 18, telescopic reversing valve 19, side shift cylinder 20, rotary lock cylinder 21, telescopic cylinder 22, electric proportional speed regulating valve 23, second safety valve 24, motor reversing valve 25, shuttle valve 26, hydraulic motor 27, brake 28, third safety valve 29, fourth safety valve 30, back pressure valve 31, boom assembly 32, rotation assembly 33, and hoisting device assembly 34. DETAILED DESCRIPTION

[0026] The core of the present invention is to provide a hydraulic system for a container front crane sling. The damping cylinder cooperates with a first electric proportional throttle valve, a second electric proportional throttle valve and a pressure reducing relief valve to achieve adjustable speed of the sling's forward and backward tilting. The forward and backward swinging speed of the sling can be adjusted during container handling, thereby improving the safety of the handling process.

[0027] In order to enable those skilled in the art to better understand the solution of the present invention, the present invention is further described in detail below in conjunction with the accompanying drawings and specific implementation methods.

[0028] Please refer to Figures 1 to 3, Figure 1 is a hydraulic principle diagram of a specific implementation of the hydraulic system of a container reach crane provided by the present invention; Figure 2 is a structural schematic diagram of a specific implementation of the hydraulic system of a container reach crane provided by the present invention; Figure 3 is a hydraulic principle diagram of the forward and backward tilting system in a specific implementation of the hydraulic system of a container reach crane provided by the present invention.

[0029] A specific embodiment of the present invention provides a hydraulic system for a container front loaders sling, which is applied to the control of the sling, wherein the sling includes a boom assembly 32, a rotating assembly 33 and a sling assembly 34, wherein the boom assembly 32 is connected to a crane body, the end of the boom assembly 32 is connected to the upper end of the rotating assembly 33, the lower end of the rotating assembly 33 is connected to the sling assembly 34, and the sling assembly 34 is used to connect a container.

[0030] The hydraulic system includes an oil source 1, an oil tank 2, a damping oil cylinder 3 and a front and rear tilt reversing valve 4. The oil source 1 provides high-pressure oil for the oil circuit. The oil tank 2 stores the hydraulic oil required by the system and receives the refluxed hydraulic oil. One end of the damping oil cylinder 3 is connected to the boom assembly 32, and the other end of the damping oil cylinder 3 is connected to the rotating assembly 33. The front and rear tilt reversing valve 4 preferably adopts a three-position four-way proportional reversing valve, and the middle position is O-type. Of course, the type of valve can also be adjusted according to the situation. The oil inlet and oil return port of the front and rear tilt reversing valve 4 are respectively connected to the oil source 1 and the oil tank 2. A working oil port of the front and rear tilt reversing valve 4 The rod chamber of the damping oil cylinder 3 is connected, and the other working oil port of the forward and backward tilt reversing valve 4 is connected to the rodless chamber of the damping oil cylinder 3. A first electric proportional throttle valve 5, a second electric proportional throttle valve 6 and a pressure relief valve 7 are also provided. The rod chamber of the damping oil cylinder 3 is connected to the rodless chamber of the damping oil cylinder 3 through the first electric proportional throttle valve 5 and the second electric proportional throttle valve 6 connected in series. The oil inlet of the pressure relief valve 7 is connected to the oil source 1, and the oil outlet of the pressure relief valve 7 is connected to the oil path between the first electric proportional throttle valve 5 and the second electric proportional throttle valve 6. The oil drain port of the pressure relief valve 7 is connected to the oil tank 2. Specifically, it includes two damping oil cylinders 3 that are arranged in parallel and move synchronously, and the rod chambers of the two damping oil cylinders 3 are connected to each other, and the rodless chambers of the two damping oil cylinders 3 are connected to each other.

[0031] Specifically, the oil inlet of the pressure reducing relief valve 7 is directly connected to the oil source 1, and the outlet pressure is set to a fixed value. When the outlet pressure is lower than the set value, the oil of the oil source 1 is reduced by the pressure reducing relief valve 7 to keep the outlet pressure at the set value. When the outlet pressure exceeds the outlet pressure set value, the outlet oil flows out through the oil drain port of the pressure reducing relief valve 7 to reduce the outlet pressure until it returns to the set value. One end of the first electric proportional throttle valve 5 is connected to the oil outlet of the pressure reducing relief valve 7, and the other end is connected to the rod chamber of the damping cylinder 3. The size of its throttling area can be controlled by the size of the electrical signal to achieve damping adjustment. Preferably, the first electric proportional throttle valve 5 has a one-way flow function when it is not powered on, and the oil can only flow from the pressure reducing relief valve 7 to the rod chamber of the damping cylinder 3 in one direction.

[0032] One end of the second electric proportional throttle valve 6 is connected to the oil outlet of the pressure reducing relief valve 7, and the other end is connected to the rodless chamber of the damping cylinder 3. The size of its throttling area can be controlled by the size of the electrical signal to achieve damping adjustment. Preferably, the second electric proportional throttle valve 6 has a one-way flow function when power is not available, and the oil can only flow in one direction from the pressure reducing relief valve 7 to the rodless chamber of the damping cylinder 3.

[0033] During the swinging process of the sling assembly 34, the damping oil cylinder 3 is in two states: extended and retracted. When the damping oil cylinder 3 is extended outward, the oil in the rod chamber of the damping oil cylinder 3 flows to the rodless chamber of the damping oil cylinder 3 through the first electric proportional throttle valve 5. Since there is an area difference between the rod chamber and the rodless chamber of the damping oil cylinder 3, the oil flowing out of the rod chamber of the damping oil cylinder 3 cannot fill the rodless chamber. At this time, the insufficient oil is replenished by the oil source 1 after being reduced in pressure by the pressure reducing relief valve 7. The extension speed of the damping oil cylinder 3 is determined by the flow rate flowing through the first electric proportional throttle valve 5, so the extension speed of the damping oil cylinder 3 can be adjusted by adjusting the first electric proportional throttle valve 5. When the damping cylinder 3 retracts inward, the oil in the rodless chamber of the damping cylinder 3 flows to the rod chamber of the damping cylinder 3 through the second electric proportional throttle valve 6. Since there is an area difference between the rod chamber and the rodless chamber of the damping cylinder 3, the oil flowing out of the rodless chamber of the damping cylinder 3 is more than the oil required by the rod chamber. At this time, the excess flow overflows through the pressure reducing relief valve 7 and flows back to the oil tank 2. The retraction speed of the damping cylinder 3 is determined by the flow through the second electric proportional throttle valve 6. Therefore, the retraction speed of the damping cylinder 3 can be adjusted by adjusting the second electric proportional throttle valve 6. During the pitching process of the boom assembly 32, the first electric proportional throttle valve 5 and the second electric proportional throttle valve 6 do not provide damping, so that the sling assembly 34 can quickly return to the horizontal position, improving the working efficiency. The sling assembly 34 actively adjusts the front and rear tilt angle. When the damping oil cylinder 3 needs to be extended, the first working position of the front and rear tilt reversing valve 4 is energized, and the oil enters the rodless chamber of the damping oil cylinder 3 through the front and rear tilt reversing valve 4, so that the damping oil cylinder 3 is extended. When the damping oil cylinder 3 needs to be retracted, the second working position of the front and rear tilt reversing valve 4 is energized, and the oil enters the rod chamber of the damping oil cylinder 3 through the front and rear tilt reversing valve 4, so that the damping oil cylinder 3 is retracted.

[0034] The specific working process is as follows: when the front crane is carrying a container, a certain electric signal is given to the first electric proportional throttle valve 5 and the second electric proportional throttle valve 6, the spreader assembly 34 will swing forward and backward, the front and rear tilt reversing valve 4 is in the middle position, and the hydraulic oil circulates in the rod chamber and the rodless chamber of the damping oil cylinder 3. Of course, the flow difference caused by the area difference is adjusted by the pressure reducing relief valve 7. During the swinging process of the spreader assembly 34, if the spreader assembly 34 swings forward too fast, the electric signal of the first electric proportional throttle valve 5 is adjusted to reduce the opening area of ​​the first electric proportional throttle valve 5, and the speed of the oil in the rod chamber of the damping oil cylinder 3 flowing to the rodless chamber of the damping oil cylinder 3 through the first electric proportional throttle valve 5 is reduced, so that the forward swing speed of the spreader assembly 34 can be reduced. If the sling assembly 34 swings backward too fast, the electric signal of the second electric proportional throttle valve 6 is adjusted to reduce the opening area of ​​the second electric proportional throttle valve 6, and the speed at which the oil in the rodless chamber of the damping oil cylinder 3 flows through the second electric proportional throttle valve 6 to the rod chamber of the damping oil cylinder 3 is reduced, thereby reducing the backward swing speed of the sling assembly 34. If both the first electric proportional throttle valve 5 and the second electric proportional throttle valve 6 are not energized, the damping oil cylinder 3 is in a locked state, that is, the sling assembly 34 will not swing forward and backward.

[0035] During the process of box alignment, if the sling assembly 34 needs to be actively tilted forward, when both the first electric proportional throttle valve 5 and the second electric proportional throttle valve 6 are not powered, the first working position of the front-rear tilt reversing valve 4 is powered, and the oil output by the oil source 1 enters the rodless chamber of the damping cylinder 3 through the front-rear tilt reversing valve 4, so that the damping cylinder 3 extends, driving the sling assembly 34 to tilt forward, and at the same time, the oil in the rod chamber of the damping cylinder 3 flows back to the oil tank 2 through the front-rear tilt reversing valve 4. When the sling assembly 34 needs to be actively tilted backward, when both the first electric proportional throttle valve 5 and the second electric proportional throttle valve 6 are not powered, the second working position of the front-rear tilt reversing valve 4 is powered, and the oil output by the oil source 1 enters the rod chamber of the damping cylinder 3 through the front-rear tilt reversing valve 4, so that the damping cylinder 3 retracts, driving the sling assembly 34 to tilt backward, and at the same time, the oil in the rodless chamber of the damping cylinder 3 flows back to the oil tank 2 through the front-rear tilt reversing valve 4.

[0036] When the boom assembly 32 drives the sling assembly 34 to lift, or when the boom assembly 32 drives the sling assembly 34 to retract inward, the sling assembly 34 will retract the damping cylinder 3. In order to make the sling assembly 34 return to the horizontal position as soon as possible, the first electric proportional throttle valve 5 must not work in the default position, and the electric signal of the second electric proportional throttle valve 6 is adjusted to keep its opening area at the maximum, thereby reducing the resistance to the retraction of the damping cylinder 3. When the boom assembly 32 drives the sling assembly 34 to descend, or when the boom assembly 32 drives the sling assembly 34 to extend outward, the sling assembly 34 will extend the damping cylinder 3. In order to make the sling assembly 34 return to the horizontal position as soon as possible, the second electric proportional throttle valve 6 must not work in the default position, and the electric signal of the first electric proportional throttle valve 5 is adjusted to keep its opening area at the maximum, thereby reducing the resistance to the extension of the damping cylinder 3.

[0037] When the front loader is transporting a container, the sling assembly 34 will swing back and forth. If the sling assembly 34 swings back and forth too fast, the corresponding electric proportional throttle valve is adjusted to reduce the opening, thereby reducing the sling assembly 34's swing speed. Compared with the traditional fixed damping method, the adjustable damping can adapt to complex and changeable vehicle usage scenarios, and the normal extension and contraction of the damping cylinder 3 is ensured by the pressure reducing relief valve 7, so that the speed of the sling assembly 34 tilting back and forth can be adjusted. Before transporting the container, the center of gravity of the container can be found, and by adjusting the center of gravity of the container to be close to the center axis of the vehicle, the possibility of rollover is greatly reduced. During the container transportation process, the sling's swing speed can be adjusted to adapt to transportation on bumpy and pothole-prone roads, and it can also operate stably in off-road environments, thereby improving the safety of the transportation process.

[0038] In order to improve safety, it also includes a first safety valve 8 and two one-way valves 9. The rod chamber and rodless chamber of the damping oil cylinder 3 are respectively connected to the inlet of the two one-way valves 9, and the outlets of the two one-way valves 9 are connected to the oil tank 2 through the first safety valve 8. If the pressure in the damping oil cylinder 3 is too high during the tilting or swinging of the sling, the oil will flow back to the oil tank 2 through the two one-way valves 9 and the first safety valve 8 to play a protective role

[0039] Please refer to FIG. 4 , which is a hydraulic principle diagram of a tilting system in a specific embodiment of a hydraulic system for a container reach stacker provided by the present invention.

[0040] In order to realize the left and right tilting of the sling and find the center of gravity of the container before transportation, the hydraulic system includes a left tilt cylinder 10, a right tilt cylinder 11 and a tilt reversing valve 12. One end of the left tilt cylinder 10 and the right tilt cylinder 11 are connected to the rotating assembly 33, and the other end is connected to the sling assembly 34. The oil inlet and oil return port of the tilt reversing valve 12 are respectively connected to the oil source 1 and the oil tank 2. One working oil port of the tilt reversing valve 12 is simultaneously connected to the rod chamber of the left tilt cylinder 10 and the rodless chamber of the right tilt cylinder 11, and the other working oil port of the tilt reversing valve 12 is simultaneously connected to the rodless chamber of the left tilt cylinder 10 and the rod chamber of the right tilt cylinder 11. At the same time, in the above manner, the movement directions of the left tilt cylinder 10 and the right tilt cylinder 11 are opposite. When the left tilt cylinder 10 extends, the right tilt cylinder 11 retracts synchronously, and vice versa. The two working oil ports of the roll reversing valve 12 are connected through a floating valve 13, and the floating valve 13 can control the conduction state of the two working oil ports of the roll reversing valve 12. Specifically, two balancing valves 16 are respectively provided at the two working oil ports of the roll reversing valve 12 for safety protection. It includes two left-side roll cylinders 10 and two right-side roll cylinders 11 that move synchronously, the rod chambers of the two left-side roll cylinders 10 and the rodless chambers of the two right-side roll cylinders 11 are connected to each other, and the rodless chambers of the two left-side roll cylinders 10 and the rod chambers of the two right-side roll cylinders 11 are connected to each other, so that the rod chambers of the cylinders on the same side are connected to the rod chambers, and the rodless chambers are connected to the rodless chambers. The roll reversing valve 12 is a three-position four-way proportional reversing valve, and the floating valve 13 is a two-position two-way reversing valve. Its on-off function determines whether the two working oil ports of the roll reversing valve 12 are connected. When both ends of the floating valve 13 are connected, the oil in the left roll cylinder 10 and the right roll cylinder 11 is in a free-flowing state. Of course, other types of valves can also be used.

[0041] Preferably, a two-way speed regulating valve 14 is also provided, and one working oil port of the roll reversing valve 12 is connected to another working oil port of the roll reversing valve 12 through a floating valve 13 and a two-way speed regulating valve 14 connected in series, and the two-way speed regulating valve 14 can keep the two-way flow constant. Furthermore, an oil drain valve 15 is also provided, one end of the oil drain valve 15 is connected to a working oil port of the roll reversing valve 12, and the other end of the oil drain valve 15 is connected to the oil tank 2. The oil drain valve 15 is a two-position two-way reversing valve. Different slings need to be frequently replaced in an off-road environment. In order to avoid oil leakage, the oil in the roll oil cylinder needs to be discharged. After the floating valve 13 is opened, the oil drain valve 15 opens under the action of gravity to discharge the high-pressure oil in the roll oil cylinder.

[0042] When the spreader assembly 34 needs to tilt to the left, the first working position of the roll reversing valve 12 is energized, and the high-pressure oil enters the rodless chamber of the left tilt oil cylinder 10 and the rod chamber of the right tilt oil cylinder 11 of the spreader assembly 34 through the roll reversing valve 12, pushing the spreader assembly 34 to tilt to the left. Accordingly, the hydraulic oil in the other chamber flows back to the oil tank 2 through the roll reversing valve 12. When the spreader assembly 34 needs to tilt to the right, the second working position of the roll reversing valve 12 is energized, and the high-pressure oil enters the rodless chamber of the right tilt oil cylinder 11 and the rod chamber of the left tilt oil cylinder 10 through the roll reversing valve 12, pushing the spreader assembly 34 to tilt to the right. Accordingly, the hydraulic oil in the other chamber flows back to the oil tank 2 through the roll reversing valve 12.

[0043] When the center of gravity of the container deviates greatly from the left and right center lines of the vehicle, the container is lifted and deviated from the ground by a certain height, and then the floating valve 13 is energized. At this time, the rod chambers of the two left tilt cylinders 10 and all the chambers of the two right tilt cylinders 11 are connected, that is, both sides are in a suspended state. Under the action of gravity, the sling assembly 34 will deviate to one side of the center of gravity of the container. In order to prevent the sling assembly 34 from tilting too fast and affecting safety, the two-way speed regulating valve 14 works at this time, so that the sling assembly 34 tilts slowly at a certain speed. After the floating valve 13 loses power, the sling assembly 34 will maintain the current tilting state, and the driver can judge the deviation direction of the center of gravity of the container by the tilting direction of the sling assembly 34. If the sling assembly 34 tilts to the left, the center of gravity of the container is biased to the left. After adjusting the sling assembly 34 to a horizontal position, the sling assembly 34 is moved to the right as a whole by one end, and the floating valve 13 is energized again for judgment. If the sling assembly 34 is still tilted to the left, it means that the center of gravity of the container is still biased to the left. Repeat the above operation. If the sling assembly 34 is tilted to the right, it means that the center of gravity of the container is biased to the right. After adjusting the sling assembly 34 to a horizontal position, move the sling assembly 34 to the left as a whole by one end, and energize the floating valve 13 again for judgment until the sling assembly 34 can remain horizontal when the floating valve 13 is energized. At this time, the gravity of the container deviating from one side is not enough to overcome the friction force of the sling assembly 34 tilting left and right, which means that the center of gravity of the container is near the center axis of the vehicle.

[0044] Please refer to FIG. 5 , which is a hydraulic principle diagram of a displacement system in a specific implementation manner of a hydraulic system for a container reach stacker provided by the present invention.

[0045] On the basis of the container reach crane hydraulic system provided in the above specific embodiments, it includes a lateral shift reversing valve 17, a rotary lock reversing valve 18 and a telescopic reversing valve 19 connected in parallel. Each reversing valve is a three-position four-way reversing valve, and the oil inlet and oil return port of each reversing valve are respectively connected to the oil source 1 and the oil tank 2, and the two working oil ports of each reversing valve are respectively connected to the two end cavities of the corresponding oil cylinder.

[0046] Furthermore, the side shift reversing valve is connected to the side shift oil cylinder 20, one end of the side shift oil cylinder 20 is connected to the rotating assembly 33, and the other end is connected to the sling assembly 34. When the sling assembly 34 needs to move to the left as a whole, the first working position of the side shift reversing valve 17 is energized, and the high-pressure oil enters the side shift oil cylinder 20 through the side shift reversing valve 17, pushing the sling assembly 34 to move to the left. When the sling assembly 34 needs to move to the right as a whole, the second working position of the side shift reversing valve 17 is energized, and the high-pressure oil enters the side shift oil cylinder 20 through the side shift reversing valve 17, pushing the sling assembly 34 to move to the right.

[0047] The rotary lock reversing valve 18 is connected to the rotary lock cylinder 21, which can push the internal connecting rod mechanism of the spreader assembly 34 to drive the spreader lock head to rotate to achieve locking and unlocking. After the spreader lock head is inserted into the container lock hole, the first working position of the rotary lock reversing valve 18 is energized, and the high-pressure oil enters the rotary lock cylinder 21 through the rotary lock reversing valve 18, pushing the spreader lock head to rotate, so that the lock head locks the container.

[0048] After the container handling is completed, the container is stacked, the second working position of the rotary lock reversing valve 18 is energized, and the high-pressure oil enters the rotary lock cylinder 21 through the rotary lock reversing valve 18 to push the sling lock head to rotate, so that the lock head can be pulled out of the container lock hole.

[0049] The telescopic reversing valve 19 is connected to the telescopic oil cylinder 22, and includes two sets of telescopic reversing valves 19 and telescopic oil cylinders 22. One end of the telescopic oil cylinder is connected to the internal box of the sling assembly 34, and the other end is connected to the main box of the sling assembly 34. The extension and retraction of the telescopic oil cylinder 22 can drive the internal box of the sling assembly 34 to move in the main box of the sling assembly 34, adapting to containers of different sizes and providing the sling assembly 34 with the function of opening and closing. When the sling assembly 34 needs to be opened, the first working position of the telescopic reversing valve 19 is energized, and the high-pressure oil enters the telescopic oil cylinder 22 through the telescopic reversing valve 19, pushing the internal box of the sling assembly 34 to extend outward. When the sling assembly 34 needs to be closed, the second working position of the telescopic reversing valve 19 is energized, and the high-pressure oil enters the telescopic oil cylinder 22 through the telescopic reversing valve 19, pushing the internal box of the sling assembly 34 to retract outward.

[0050] When the speed of the spreader assembly 34 needs to be adjusted for extension and retraction and left and right movement, an electric proportional speed regulating valve 23 is provided, and the oil source 1 is connected to the oil inlet of the side shift reversing valve 17, the rotary lock reversing valve 18 and the telescopic reversing valve 19 through the electric proportional speed regulating valve 23, and a second safety valve 24 is provided at the outlet of the electric proportional speed regulating valve 23. The action speed can be adjusted by adjusting the electric signal of the electric proportional speed regulating valve 23. When the working pressure of the spreader assembly 34 is too high when it is unlocked, locked, extended, retracted, moved left as a whole, and moved right as a whole, part of the oil flows back to the oil tank 2 through the second safety valve 24.

[0051] During the overload process, the high-pressure oil output by the oil source 1 enters each reversing valve through the electric proportional speed control valve 23, and the telescopic movement of the corresponding oil cylinder is controlled by adjusting the reversing valve. At the same time, the oil in the other cavity flows back to the oil tank 2 through the reversing valve.

[0052] Please refer to FIG. 6 , which is a hydraulic principle diagram of a motor system in a specific embodiment of the hydraulic system for a container reach stacker provided by the present invention.

[0053] Furthermore, it includes a motor reversing valve 25, a shuttle valve 26, a hydraulic motor 27 and a brake 28. The two oil ports of the hydraulic motor 27 are connected with a third safety valve 29 and a fourth safety valve 30 in parallel. The third safety valve 29 and the fourth safety valve 30 flow in opposite directions to prevent the working pressure of the hydraulic motor 27 from being too high. The return oil port of the motor reversing valve 25 is provided with a back pressure valve 31. The rotation of the hydraulic motor 27 can drive the rotating assembly 33 to rotate. The motor reversing valve 25 is an electric proportional three-position four-way reversing valve. Its working oil port is connected to the working oil port of the hydraulic motor 27. The switching of the left and right positions of the motor reversing valve 25 can realize the control of the rotation direction of the hydraulic motor 27. When the rotation speed needs to be adjusted, the electrical signal of the motor reversing valve 25 can be adjusted. The brake 28 is a normally closed type. It provides braking force in the absence of oil to prevent the sling assembly 34 from rotating. After the oil reaches the release pressure, the brake 28 is opened and the sling assembly 34 can rotate. The two comparison ports of shuttle valve 26 are respectively connected to the two working oil ports of hydraulic motor 27, and its outlet is connected to brake 28, so that the high-pressure oil driving the hydraulic motor 27 to rotate can be selected through shuttle valve 26 and introduced into brake 28, and brake 28 is opened to allow the hydraulic motor 27 to rotate. Back pressure valve 31 is placed between the oil return port of motor reversing valve 25 and oil tank 2. When the oil return of motor reversing valve 25 exceeds its set pressure, the oil can return to the oil tank to prevent the hydraulic motor 27 from sucking air.

[0054] When the sling assembly 34 needs to rotate clockwise, the motor reversing valve 25 is energized in the left position, and the high-pressure oil passes through the motor reversing valve 25 and the shuttle valve 26 in sequence to enter the brake 28, opening the brake 28 so that the sling assembly 34 can rotate. Another oil path enters the hydraulic motor 27 through the motor reversing valve 25, causing the hydraulic motor 27 to rotate clockwise and drive the sling assembly 34 to rotate clockwise. When the sling assembly 34 needs to rotate counterclockwise, the motor reversing valve 25 is energized in the right position, and the high-pressure oil passes through the motor reversing valve 25 and the shuttle valve 26 in sequence to enter the brake 28, opening the brake 28 so that the sling assembly 34 can rotate. Another oil path enters the hydraulic motor 27 through the motor reversing valve 25, causing the hydraulic motor 27 to rotate counterclockwise and drive the sling assembly 34 to rotate counterclockwise.

[0055] In the above specific embodiments, adjusting the number and grouping of each cylinder and adjusting the type and control method of each valve according to the situation are all within the protection scope of the present invention. The selection in the above embodiments is only a preferred solution, and other types can also be used.

[0056] The above is a detailed introduction to the container reach stacker hydraulic system provided by the present invention. This article uses specific examples to illustrate the principles and implementation methods of the present invention. The description of the above embodiments is only used to help understand the method and core ideas of the present invention. It should be pointed out that for ordinary technicians in this technical field, without departing from the principles of the present invention, the present invention can also be improved and modified in a number of ways, and these improvements and modifications also fall within the scope of protection of the claims of the present invention.

Claims

1. A container reach stacker hydraulic system, comprising an oil source (1), an oil tank (2), a damping oil cylinder (3) and a forward and backward tilt reversing valve (4), wherein one end of the damping oil cylinder (3) is connected to a boom assembly (32), and the other end of the damping oil cylinder (3) is connected to a rotating assembly (33), characterized in that: The oil inlet and oil return port of the forward and backward tilting reversing valve (4) are respectively connected to the oil source (1) and the oil tank (2); the two working oil ports of the forward and backward tilting reversing valve (4) are respectively connected to the rod chamber and the rodless chamber of the damping oil cylinder (3); the valve further comprises a first electric proportional throttle valve (5), a second electric proportional throttle valve (6) and a pressure reducing relief valve (7); the rod chamber of the damping oil cylinder (3) is connected to the rodless chamber of the damping oil cylinder (3) via the first electric proportional throttle valve (5) and the second electric proportional throttle valve (6) connected in series; the oil inlet of the pressure reducing relief valve (7) is connected to the oil source (1); the oil outlet of the pressure reducing relief valve (7) is connected to the oil path between the first electric proportional throttle valve (5) and the second electric proportional throttle valve (6); and the oil drain port of the pressure reducing relief valve (7) is connected to the oil tank (2); If the lifting device assembly (34) swings forward too fast, the electrical signal of the first electrical proportional throttle valve (5) is adjusted to reduce the opening area of ​​the first electrical proportional throttle valve (5), and the speed at which the oil in the rod chamber of the damping oil cylinder (3) flows through the first electrical proportional throttle valve (5) to the rodless chamber of the damping oil cylinder (3) is reduced, thereby reducing the forward swing speed of the lifting device assembly (34); if the lifting device assembly (34) swings backward too fast, the electrical signal of the second electrical proportional throttle valve (6) is adjusted to reduce the opening area of ​​the second electrical proportional throttle valve (6), and the speed at which the oil in the rodless chamber of the damping oil cylinder (3) flows through the second electrical proportional throttle valve (6) to the rod chamber of the damping oil cylinder (3) is reduced, thereby reducing the backward swing speed of the lifting device assembly (34); if both the first electrical proportional throttle valve (5) and the second electrical proportional throttle valve (6) are not energized, the damping oil cylinder (3) is in a locked state, and the lifting device assembly (34) will not swing forward or backward; When the boom assembly (32) drives the sling assembly (34) to rise, or when the boom assembly (32) drives the sling assembly (34) to retract inward, the sling assembly (34) will cause the damping cylinder (3) to retract, and the first electric proportional throttle valve (5) must not work in a default position, and the electric signal of the second electric proportional throttle valve (6) is adjusted to keep its opening area at the maximum, thereby reducing the resistance to the retraction of the damping cylinder (3); when the boom assembly (32) drives the sling assembly (34) to descend, or when the boom assembly (32) drives the sling assembly (34) to extend outward, the sling assembly (34) will cause the damping cylinder (3) to extend, and the second electric proportional throttle valve (6) must not work in a default position, and the electric signal of the first electric proportional throttle valve (5) is adjusted to keep its opening area at the maximum, thereby reducing the resistance to the extension of the damping cylinder (3); It comprises a left tilt oil cylinder (10), a right tilt oil cylinder (11) and a tilt reversing valve (12), wherein one end of the left tilt oil cylinder (10) and the right tilt oil cylinder (11) are connected to the rotating assembly (33), and the other end is connected to the sling assembly (34), the oil inlet and the oil return port of the tilt reversing valve (12) are respectively connected to the oil source (1) and the oil tank (2), one working oil port of the tilt reversing valve (12) is simultaneously connected to the rod chamber of the left tilt oil cylinder (10) and the rodless chamber of the right tilt oil cylinder (11), the other working oil port of the tilt reversing valve (12) is simultaneously connected to the rodless chamber of the left tilt oil cylinder (10) and the rod chamber of the right tilt oil cylinder (11), the two working oil ports of the tilt reversing valve (12) are connected via a floating valve (13), and the floating valve (13) can control the conduction state of the two working oil ports of the tilt reversing valve (12); It also comprises a two-way speed regulating valve (14), wherein one working oil port of the roll reversing valve (12) is connected to another working oil port of the roll reversing valve (12) via the floating valve (13) and the two-way speed regulating valve (14) connected in series, and the two-way speed regulating valve (14) is capable of maintaining a constant two-way flow rate.

2. The container reach stacker hydraulic system according to claim 1, characterized in that: It also includes a first safety valve (8) and two one-way valves (9), wherein the rod chamber and the rodless chamber of the damping oil cylinder (3) are respectively connected to the inlets of the two one-way valves (9), and the outlets of the two one-way valves (9) are connected to the oil tank (2) through the first safety valve (8).

3. The container reach stacker hydraulic system according to claim 2, characterized in that: It comprises two damping oil cylinders (3) which are arranged in parallel and move synchronously, the rod chambers of the two damping oil cylinders (3) being connected to each other, and the rodless chambers of the two damping oil cylinders (3) being connected to each other.

4. The container reach stacker hydraulic system according to claim 1, characterized in that: It also comprises an oil drain valve (15), one end of the oil drain valve (15) being connected to a working oil port of the roll reversing valve (12), and the other end of the oil drain valve (15) being connected to the oil tank (2).

5. The container reach stacker hydraulic system according to claim 4, characterized in that: Two balancing valves (16) are respectively arranged at the two working oil ports of the roll reversing valve (12).

6. The container reach stacker hydraulic system according to claim 5, characterized in that: It comprises two left tilt oil cylinders (10) and two right tilt oil cylinders (11) which move synchronously, the rod chambers of the two left tilt oil cylinders (10) and the rodless chambers of the two right tilt oil cylinders (11) being connected to each other, and the rodless chambers of the two left tilt oil cylinders (10) and the rod chambers of the two right tilt oil cylinders (11) being connected to each other.

7. The container reach stacker hydraulic system according to any one of claims 1 to 6, characterized in that: The invention comprises a lateral shift reversing valve (17), a rotary lock reversing valve (18) and a telescopic reversing valve (19) which are connected in parallel with each other, wherein the lateral shift reversing valve is connected to a lateral shift oil cylinder (20), the rotary lock reversing valve (18) is connected to a rotary lock oil cylinder (21), and the telescopic reversing valve (19) is connected to a telescopic oil cylinder (22); the oil source (1) is connected to the oil inlets of the lateral shift reversing valve (17), the rotary lock reversing valve (18) and the telescopic reversing valve (19) via an electric proportional speed regulating valve (23), and a second safety valve (24) is provided at the outlet of the electric proportional speed regulating valve (23).

8. The container reach stacker hydraulic system according to claim 7, characterized in that: The invention comprises a motor reversing valve (25), a shuttle valve (26), a hydraulic motor (27) and a brake (28); two oil ports of the hydraulic motor (27) are connected to a third safety valve (29) and a fourth safety valve (30) connected in parallel; the third safety valve (29) and the fourth safety valve (30) have opposite flow directions; and a back pressure valve (31) is provided at the oil return port of the motor reversing valve (25).

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