Hydraulic control system

Abstract

The utility model discloses a hydraulic control system, and relates to the technical field of unloading, the hydraulic control system is applied to an unloading platform, the unloading platform is used for driving in or driving out of an unloading machine, the hydraulic control system comprises a main oil cylinder assembly, a main oil cylinder control unit, a system control unit and a synchronous deviation rectifying unit, the main oil cylinder assembly is fixedly arranged on the side, close to the ground, of the unloading platform and is in driving connection with the unloading platform. The main oil cylinder control unit is arranged on the side, close to the ground, of the main oil cylinder assembly and connected with the main oil cylinder assembly and the hydraulic oil tank. The system control unit is arranged on the side, close to the ground, of the main oil cylinder control unit and connected with the main oil cylinder control unit and the hydraulic oil tank. The synchronous deviation rectifying unit is arranged between the main oil cylinder control unit and the main oil cylinder assembly and connected with the main oil cylinder assembly and the hydraulic oil tank. According to the technical scheme, the problem that an existing unloading platform cannot be lifted synchronously is solved.

Description

Technical Field

[0001] This utility model relates to the field of unloading technology, and in particular to a hydraulic control system. Background Technology

[0002] Mobile unloading machines, as important equipment in the field of bulk material handling, are widely used in places requiring multi-point unloading operations, such as thermal power plants and port terminals, due to their flexible mobility. Currently, most mobile unloading machines on the market use hydraulic drive systems, with each hydraulic cylinder working independently; however, there is a lack of effective synchronization control mechanisms between these cylinders.

[0003] This type of hydraulic lifting structure has some problems in practical applications. When performing lifting or lowering operations, the actions of each hydraulic cylinder are not synchronized due to manufacturing errors, oil circuit pressure drop and other factors. This can easily cause the equipment to tilt, and in severe cases, it may cause the entire equipment to overturn. Especially during long-term continuous operation, the asynchronous phenomenon will continue to intensify, seriously affecting the work efficiency and increasing the equipment maintenance cost. Utility Model Content

[0004] The main purpose of this invention is to propose a hydraulic control system that aims to solve the problem that existing unloading platforms cannot lift and lower synchronously.

[0005] To achieve the above objectives, the present invention proposes a hydraulic control system applied to an unloading platform, which is used for the entry and exit of the unloading machine. The hydraulic control system includes:

[0006] The main hydraulic cylinder assembly is fixed to the side of the unloading platform near the ground and is driven to the unloading platform.

[0007] The main cylinder control unit is located on the side of the main cylinder assembly closest to the ground and is connected to the main cylinder assembly and the hydraulic oil tank.

[0008] A system control unit is located on the side of the main cylinder control unit closest to the ground, and is connected to the main cylinder control unit and the hydraulic oil tank; and

[0009] A synchronous correction unit is located between the main cylinder control unit and the main cylinder assembly, and is connected to the main cylinder assembly and the hydraulic oil tank.

[0010] In one embodiment, the main hydraulic cylinder assembly includes a first main hydraulic cylinder and a second main hydraulic cylinder, and the synchronous correction unit includes:

[0011] Synchronous motor, wherein the oil inlet of the synchronous motor is the same as the oil inlet of the synchronous motor in the main cylinder control unit;

[0012] A first piping assembly connects the synchronous motor and the first master cylinder, and the first piping assembly is equipped with a first pressure reducing valve and a first solenoid ball valve; and

[0013] The second pipeline assembly connects the synchronous motor and the second main cylinder, and the second pipeline assembly is equipped with a second pressure reducing valve and a second solenoid ball valve.

[0014] In one embodiment, the first piping assembly includes a first main pipe and a first branch pipe. The first main pipe connects the synchronous motor and the first main cylinder, and the first main pipe is connected to the hydraulic tank through the first branch pipe. The first pressure reducing valve and the first solenoid ball valve are both disposed on the first branch pipe. The second piping assembly includes a second main pipe and a second branch pipe. The second main pipe connects the synchronous motor and the second main cylinder, and the second main pipe is connected to the hydraulic tank through the second branch pipe. The second pressure reducing valve and the second solenoid ball valve are both disposed on the second branch pipe.

[0015] In one embodiment, a first throttle valve is further provided between the first pressure reducing valve and the first solenoid ball valve, and the feedback port of the first pressure reducing valve is connected to the outlet port of the first throttle valve. A second throttle valve is further provided between the second pressure reducing valve and the second solenoid ball valve, and the feedback port of the second pressure reducing valve is connected to the outlet port of the second throttle valve.

[0016] In one embodiment, the first branch pipe and the second branch pipe share a portion of the pipeline, and the synchronous correction unit further includes a third electromagnetic ball valve, which is located on the shared pipeline.

[0017] In one embodiment, the hydraulic control system further includes an inclinometer, which is mounted on the unloading platform, and both the first electromagnetic ball valve and the second electromagnetic ball valve are electrically connected to the inclinometer.

[0018] In one embodiment, the system control unit includes a main oil circuit, a first check valve, and a solenoid relief valve. The main oil circuit is connected to the main cylinder control unit and the hydraulic oil tank. The first check valve and the solenoid relief valve are both located on the main oil circuit, and the oil inlet of the solenoid relief valve is connected to the oil outlet of the first check valve.

[0019] In one embodiment, the system control unit further includes a third pipeline, an air cooler, and a second check valve. The third pipeline connects the hydraulic oil tank and the main oil circuit. The outlet of the electromagnetic relief valve is connected to the hydraulic oil tank through the third pipeline. The air cooler is located on the third pipeline, and the second check valve is connected in parallel with the air cooler.

[0020] In one embodiment, the hydraulic control system further includes a wheel chock control unit and a wheel chock cylinder. The wheel chock control unit is connected to the wheel chock cylinder and the hydraulic oil tank. The wheel chock control unit includes a first solenoid directional valve, a hydraulic lock, and a first double one-way throttle valve.

[0021] In one embodiment, the hydraulic control system further includes a front wheel control unit, a rear wheel control unit, a front wheel lifting cylinder, and a rear wheel lifting cylinder. The front wheel control unit is connected to the front wheel lifting cylinder and the hydraulic oil tank, and the rear wheel control unit is connected to the rear wheel lifting cylinder and the hydraulic oil tank. Both the front wheel control unit and the rear wheel control unit include a second solenoid directional valve, a balance valve, a second double one-way throttle valve, and a second shut-off valve.

[0022] The technical solution of this utility model involves setting a synchronous correction unit between the main cylinder control unit and the main cylinder assembly, with both ends of the synchronous correction unit connected to the main cylinder assembly and the hydraulic oil tank, respectively. When multiple main cylinder assemblies are working on the unloading platform (e.g., a large unloading platform may have multiple cylinders working in coordination), the synchronous correction unit ensures that the movements of each main cylinder assembly remain synchronized, thereby guaranteeing the synchronous rising and falling of the unloading platform and preventing tipping during operation. It can monitor the working status of each main cylinder assembly in real time, and if a deviation in movement is detected between a main cylinder assembly and other components, it can make timely adjustments to ensure the overall stability of the unloading platform and prevent problems such as tilting and jamming caused by cylinder asynchrony. Attached Figure Description

[0023] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0024] Figure 1 A general diagram of the control system of an embodiment of the hydraulic control system provided by this utility model;

[0025] Figure 2 A schematic diagram of the structure of the main cylinder assembly and the synchronous correction unit in one embodiment of the hydraulic control system provided by this utility model;

[0026] Figure 3 A schematic diagram of the system control unit in another embodiment of the hydraulic control system provided by this utility model;

[0027] Figure 4A schematic diagram of the control unit for the wheel chock in another embodiment of the hydraulic control system provided by this utility model;

[0028] Figure 5 A schematic diagram of the front wheel control unit in another embodiment of the hydraulic control system provided by this utility model;

[0029] Figure 6 A schematic diagram of the main cylinder control unit in another embodiment of the hydraulic control system provided by this utility model.

[0030] Explanation of icon numbers:

[0031] 100. Hydraulic Control System; 01. Hydraulic Oil Tank; 1. Main Cylinder Assembly; 11. First Main Cylinder; 12. Second Main Cylinder; 2. Main Cylinder Control Unit; 21. Inlet Side Two-Way Directional Valve; 22. Return Side Two-Way Directional Valve; 23. First Shut-Off Valve; 3. System Control Unit; 31. Main Oil Circuit; 32. First Check Valve; 33. Solenoid Relief Valve; 34. Third Pipeline; 35. Air Cooler; 36. Second Check Valve; 4. Synchronous Correction Unit; 41. Synchronous Motor; 42. First Pipeline Assembly; 421. First Main Pipe; 422. First Branch Pipe; 423. First Pressure Reducing Valve; 424. First... 425. Electromagnetic ball valve; 43. First throttle valve; 44. Second pipeline assembly; 45. Second main pipe; 46. Second branch pipe; 47. Second pressure reducing valve; 48. Second electromagnetic ball valve; 49. Second throttle valve; 40. Third electromagnetic ball valve; 51. Wheel chock control unit; 52. First electromagnetic directional valve; 53. Hydraulic lock; 54. First double one-way throttle valve; 65. Wheel chock cylinder; 66. Front wheel control unit; 67. Second electromagnetic directional valve; 68. Balance valve; 69. Second double one-way throttle valve; 70. Second shut-off valve; 81. Rear wheel control unit; 92. Front wheel lifting cylinder; 10. Rear wheel lifting cylinder.

[0032] Hydraulic oil tank;

[0033] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0034] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present utility model.

[0035] It should be noted that if the embodiments of this utility model involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0036] Furthermore, if the embodiments of this utility model involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this utility model.

[0037] Existing multi-cylinder combined hydraulic lifting structures have some problems in practical applications. When performing lifting or lowering operations, the actions of each hydraulic cylinder may be asynchronous due to manufacturing errors, oil circuit pressure drop, and other factors. This can easily cause equipment tilting, and in severe cases, it may cause a safety accident of the entire equipment overturning. Especially during long-term continuous operation, the asynchronous phenomenon will continue to intensify, seriously affecting the work efficiency and increasing the equipment maintenance cost.

[0038] This utility model proposes a hydraulic control system applied to an unloading platform, which is used for the unloading machine to enter or leave.

[0039] Please see Figure 1 and Figure 6 In one embodiment of this utility model, the hydraulic control system 100 includes:

[0040] The main hydraulic cylinder assembly 1 is fixed on the side of the unloading platform near the ground and is connected to the unloading platform drive.

[0041] The main cylinder control unit 2 is located on the side of the main cylinder assembly 1 closest to the ground and is connected to the main cylinder assembly 1 and the hydraulic oil tank 01.

[0042] System control unit 3 is located on the side of main cylinder control unit 2 closest to the ground, and connects main cylinder control unit 2 and hydraulic oil tank 01; and

[0043] The synchronous correction unit 4 is located between the main cylinder control unit 2 and the main cylinder assembly 1, and is connected to the main cylinder assembly 1 and the hydraulic oil tank 01.

[0044] The technical solution of this utility model involves setting a synchronous correction unit 4 between the main cylinder control unit 2 and the main cylinder assembly 1, with the two ends of the synchronous correction unit 4 connected to the main cylinder assembly 1 and the hydraulic oil tank 01, respectively. When multiple main cylinder assemblies 1 are working on the unloading platform (e.g., a large unloading platform may have multiple cylinders working in coordination), the synchronous correction unit 4 can ensure that the actions of each main cylinder assembly 1 remain synchronized. It can monitor the working status of each main cylinder assembly 1 in real time, and once it detects a deviation in action between a certain main cylinder assembly 1 and other components, it can make timely adjustments to ensure the overall stability of the unloading platform and avoid problems such as tilting and jamming of the unloading platform caused by cylinder asynchrony.

[0045] Specifically, the synchronous correction unit 4 can be either a hydraulic or electrical synchronous correction structure. The hydraulic synchronous correction structure can utilize a proportional valve and sensors to achieve synchronous correction. The proportional valve adjusts the flow and pressure of the hydraulic oil based on the signals fed back from the sensors, ensuring synchronized movement of each actuator. The sensors monitor the position or speed of the actuators in real time and feed the signals back to the proportional valve for adjustment. The electrical synchronous correction structure can utilize a PLC (Programmable Logic Controller) and a driver to achieve electrical synchronous correction. The PLC calculates the control signals for each actuator based on the set synchronization parameters and the signals fed back from the sensors, and sends them to the driver. The driver controls the motor's speed and torque, thereby achieving synchronized movement of the actuators. The specific structure type of the correction unit can be selected and set according to actual needs. It should be noted that there is no specific limitation on the number of main cylinders in the main cylinder group; it can be selected and set according to the size of the unloading platform and the weight of the unloading machine.

[0046] During the unloading process, the system control unit 3 can coordinate and control the entire hydraulic control system 100 as a whole. By receiving various sensor signals (such as the tilt sensor of the unloading platform, the cylinder pressure sensor, etc.), the system control unit 3 can accurately control the adjustment of the hydraulic oil by the main cylinder control unit 2 according to the preset program and algorithm, thereby realizing the coordinated control of the main cylinder assembly 1, making the various actions of the unloading platform (such as lifting, tilting, etc.) more stable and precise.

[0047] In the embodiments of this utility model, please refer to Figure 1 and Figure 2 The main hydraulic cylinder assembly 1 includes a first main hydraulic cylinder 11 and a second main hydraulic cylinder 12, and the synchronous correction unit 4 includes:

[0048] Synchronous motor 41, the oil inlet of synchronous motor 41 is connected to the oil inlet of synchronous motor 41 of main cylinder control unit 2;

[0049] The first pipeline assembly 42 connects the synchronous motor 41 and the first main cylinder 11, and the first pipeline assembly 42 is equipped with a first pressure reducing valve 423 and a first solenoid ball valve 424; and

[0050] The second pipeline assembly 43 is connected to the synchronous motor 41 and the second main cylinder 12, and the second pipeline assembly 43 is provided with a second pressure reducing valve 433 and a second solenoid ball valve 434.

[0051] Specifically, the oil inlet of the synchronous motor 41 is connected to the oil outlet of the main cylinder control unit 2. One oil outlet of the synchronous motor 41 is connected to the first main cylinder 11 through the first pipeline assembly 42, and the other oil outlet of the synchronous motor 41 is connected to the second main cylinder 12 through the second pipeline assembly 43. The hydraulic oil flowing out of the synchronous motor 41 is divided into two paths. One path flows to the first main cylinder 11 through the first pipeline assembly 42, and the other path flows to the second main cylinder 12 through the second pipeline assembly 43. In the first pipeline assembly 42, the hydraulic oil first passes through the first pressure reducing valve 423, which can regulate the pressure of the hydraulic oil, and then passes through the first solenoid ball valve 424. The first solenoid ball valve 424 can control whether the hydraulic oil passes through according to the control signal of the system, thereby controlling the working state of the first main cylinder 11 (such as start, stop, working speed, etc.). Similarly, in the second pipeline assembly 43, the hydraulic oil first passes through the second pressure reducing valve 433 to regulate the pressure, and then passes through the second solenoid ball valve 434 to control the working state of the second main cylinder 12.

[0052] When the working states of the first master cylinder 11 and the second master cylinder 12 become asynchronous due to some reason (such as load difference, slight difference in the cylinder itself, etc.), the synchronous motor 41 will adjust according to system feedback. For example, if the extension and retraction speed of the first master cylinder 11 is faster than that of the second master cylinder 12, the synchronous motor 41 will adjust the distribution of hydraulic oil. This may be done by changing the pressure setting of the first pressure reducing valve 423 and the second pressure reducing valve 433 or by controlling the opening and closing degree of the first solenoid ball valve 424 and the second solenoid ball valve 434, thereby slowing down the speed of the first master cylinder 11 or speeding up the speed of the second master cylinder 12, thus achieving synchronous correction between the two.

[0053] It should be noted that the main cylinder control unit 2 may include an inlet-side two-way directional valve 21 and a return-side two-way directional valve 22. The inlet-side two-way directional valve 21 is controlled by a shuttle valve. Port B of the inlet-side two-way directional valve 21 is connected to the outlet of the system control unit 3, and port A of the inlet-side two-way directional valve 21 is connected to the inlet of the synchronous motor 41 through a one-way throttle valve. Port A of the return-side two-way directional valve 22 is connected to the inlet of the synchronous motor 41 through a one-way throttle valve, and port B of the return-side two-way directional valve 22 is connected to the oil tank. When YV2 of the inlet-side two-way directional valve 21 is energized, ports A and B of the inlet-side two-way directional valve 21 are connected. When YV3 of the return-side two-way directional valve 22 is energized, ports A and B of the return-side two-way directional valve 22 are connected. In addition, the main cylinder control unit 2 also includes a first shut-off valve 23 connected in parallel with the return oil side two-way reversing valve 22. The first shut-off valve 23 serves as an emergency manual valve. When the system experiences an unexpected power failure, the unloading platform can be lowered by opening the first shut-off valve 23.

[0054] In the embodiments of this utility model, please refer to Figure 2 The first pipeline assembly 42 includes a first main pipe 421 and a first branch pipe 422. The first main pipe 421 connects the synchronous motor 41 and the first main cylinder 11, and the first main pipe 421 is connected to the hydraulic oil tank 01 through the first branch pipe 422. A first pressure reducing valve 423 and a first solenoid ball valve 424 are both located on the first branch pipe 422. When it is necessary to control the working state of the first main cylinder 11, the first pressure reducing valve 423 and the first solenoid ball valve 424 located on the first branch pipe 422 function. The first pressure reducing valve 423 adjusts the pressure of the hydraulic oil in the first branch pipe 422, and the first solenoid ball valve 424 controls the flow of hydraulic oil in the first branch pipe 422. If the first main cylinder 11 is to extend slowly, the first pressure reducing valve 423 will appropriately reduce the hydraulic oil pressure in the first branch pipe 422, and the first solenoid ball valve 424 will open, so that the hydraulic oil after pressure adjustment flows through the connection point between the first branch pipe 422 and the first main pipe 421 to the first main cylinder 11, thereby controlling the extension speed of the first main cylinder 11.

[0055] Similarly, the second piping assembly 43 includes a second main pipe 431 and a second branch pipe 432. The second main pipe 431 connects to the synchronous motor 41 and the second main cylinder 12, and the second main pipe 431 is connected to the hydraulic oil tank 01 through the second branch pipe 432. The second pressure reducing valve 433 and the second solenoid ball valve 434 are both located on the second branch pipe 432. For the second main cylinder 12, the second pressure reducing valve 433 and the second solenoid ball valve 434 operate in a similar manner on the second branch pipe 432. When the working state of the second main cylinder 12 needs to be adjusted, the second pressure reducing valve 433 adjusts the pressure, and the second solenoid ball valve 434 controls the flow of hydraulic oil, thereby controlling the extension and retraction speed, start and stop operations of the second main cylinder 12.

[0056] During operation, if a master cylinder (such as the first master cylinder 11) needs to retract or adjust its working state, resulting in some hydraulic oil needing to flow back, the hydraulic oil can flow back to the hydraulic oil tank 01 through the connection between the first main pipe 421 and the first branch pipe 422. Similarly, hydraulic oil that needs to flow back when the second master cylinder 12 is working can also flow back to the hydraulic oil tank 01 through the connection between the second main pipe 431 and the second branch pipe 432. This design helps maintain the pressure balance of the entire hydraulic system and the recycling of hydraulic oil.

[0057] In the embodiments of this utility model, please refer to Figure 2 A first throttle valve 425 is also provided between the first pressure reducing valve 423 and the first solenoid ball valve 424. The feedback port of the first pressure reducing valve 423 is connected to the outlet of the first throttle valve 425. A second throttle valve 435 is also provided between the second pressure reducing valve 433 and the second solenoid ball valve 434. The feedback port of the second pressure reducing valve 433 is connected to the outlet of the second throttle valve 435. In the first pipeline assembly 42, the hydraulic oil after passing through the first pressure reducing valve 423 enters the first throttle valve 425. The first throttle valve 425 precisely controls the flow rate of the hydraulic oil by changing the size of its throttle orifice. Since the feedback port of the first pressure reducing valve 423 is connected to the outlet of the first throttle valve 425, when the hydraulic oil flow rate or pressure at the outlet of the first throttle valve 425 changes, the first pressure reducing valve 423 will readjust according to this feedback information. For example, if the hydraulic oil pressure at the outlet of the first throttle valve 425 decreases for some reason (such as load change), the first pressure reducing valve 423 will appropriately reduce the pressure reduction to maintain a stable hydraulic oil pressure supply to the first master cylinder 11. In the second pipeline assembly 43, the hydraulic oil after passing through the second pressure reducing valve 433 enters the second throttle valve 435. The second throttle valve 435 precisely controls the hydraulic oil flow rate, and the second pressure reducing valve 433 performs a similar readjustment based on feedback information from the outlet of the second throttle valve 435 to ensure stable hydraulic oil pressure and flow rate supplied to the second master cylinder 12. The throttle valve can be a needle valve, which changes the size of the throttle orifice by rotating the screw of the needle valve, thereby precisely controlling the hydraulic oil flow rate. The first pressure reducing valve 423 and the second pressure reducing valve 433 can be pilot-operated pressure reducing valves, which control the pressure reduction action of the main valve through a pilot valve.

[0058] In the embodiments of this utility model, please refer to Figure 2The first branch pipe 422 and the second branch pipe 432 share a portion of the pipeline. The synchronous correction unit 4 also includes a third solenoid ball valve 44, which is located on the shared pipeline. The third solenoid ball valve 44 can be a two-position three-way solenoid ball valve or a direct-acting solenoid ball valve. The purpose of setting the third solenoid ball valve 44 is to prevent the first solenoid ball valve 424 or the second solenoid ball valve 434 from being in a normally open state when the valve is faulty or stuck. In this case, the main oil cylinder on this side would be directly connected to the oil tank through the faulty valve, causing the platform to tip over.

[0059] In an embodiment of this utility model, the hydraulic control system 100 further includes an inclinometer (not shown), which is mounted on the unloading platform. The first electromagnetic ball valve 424 and the second electromagnetic ball valve 434 are both electrically connected to the inclinometer. The inclinometer can be a capacitive inclinometer or an accelerometer-type inclinometer. When the tilt angle of the unloading platform reaches a preset value (e.g., 0.5°), the electromagnetic ball valve (first electromagnetic ball valve 424 or second electromagnetic ball valve 434) of the main cylinder on the side that rises faster opens, and the excess hydraulic oil in the faster-rising main cylinder returns to the hydraulic oil tank 01, thus making the rising speed of the two main cylinders consistent. By setting a synchronous correction unit 4, leveling and correction can be performed in real time during the lifting and lowering of the unloading platform, ensuring the synchronous operation of the two main cylinders.

[0060] In the embodiments of this utility model, please refer to Figure 3 The system control unit 3 includes a main oil circuit 31, a first check valve 32, and a solenoid relief valve 33. The main oil circuit 31 connects the main cylinder control unit 2 and the hydraulic oil tank 01. Both the first check valve 32 and the solenoid relief valve 33 are located on the main oil circuit 31, and the inlet of the solenoid relief valve 33 is connected to the outlet of the first check valve 32. The system control unit 3 is used to control the pressure of the entire system, keeping the hydraulic system in a zero-pressure state (non-working state) or a pressurized state (working state). The first check valve 32 can be a cone valve or a ball valve, and the solenoid relief valve 33 can be a pilot-operated solenoid relief valve or a direct-acting solenoid relief valve. In the main oil circuit 31, the hydraulic oil first passes through the first check valve 32, which allows the hydraulic oil to flow from the direction of the main cylinder control unit 2 to the direction of the solenoid relief valve 33, while preventing the hydraulic oil from flowing in the opposite direction. After passing through the first check valve 32, the hydraulic oil enters the inlet of the solenoid relief valve 33. When the system pressure exceeds the set value, the solenoid relief valve 33 will open, allowing the excess hydraulic oil to flow back to the hydraulic oil tank 01 through the solenoid relief valve 33, thereby protecting the entire hydraulic system from damage caused by excessive pressure.

[0061] In the embodiments of this utility model, please refer to Figure 3The system control unit 3 also includes a third pipeline 34, an air cooler 35, and a second check valve 36. The third pipeline 34 connects the hydraulic oil tank 01 and the main oil circuit 31. The outlet of the solenoid relief valve 33 is connected to the hydraulic oil tank 01 through the third pipeline 34. The air cooler 35 is installed on the third pipeline 34, and the second check valve 36 is connected in parallel with the air cooler 35. In the main oil circuit 31, the hydraulic oil first passes through the first check valve 32 and then enters the solenoid relief valve 33. When the system pressure exceeds the set value, the solenoid relief valve 33 opens, allowing excess hydraulic oil to flow to the hydraulic oil tank 01 through the third pipeline 34. The air cooler 35 can be a finned tube type or a plate-fin type, and the second check valve 36 can be a cone valve type or a butterfly check valve. The hydraulic oil flowing out of the outlet of the solenoid relief valve 33 will pass through the air cooler 35 during its return to the hydraulic oil tank 01. The air cooler 35 cools the hydraulic oil by means of air cooling.

[0062] In the embodiments of this utility model, please refer to Figure 4 The hydraulic control system 100 also includes a wheel chock control unit 5 and a wheel chock cylinder 54. The wheel chock control unit 5 is connected to the wheel chock cylinder 54 and the hydraulic oil tank 01. The wheel chock control unit 5 includes a first solenoid directional valve 51, a hydraulic lock 52, and a first double one-way throttle valve 53. The wheel chock control unit 5 is used to control the extension and retraction of the wheel chock cylinder 54 to control the raising and lowering of the wheel chock, thereby restricting the wheels of the vehicle. When the YV4 of the first solenoid directional valve 51 is energized, the P port and B port of the first solenoid directional valve 51 are connected, and the A port and T port are connected, thereby lowering the wheel chock cylinder 54. When the YV5 of the first solenoid directional valve 51 is energized, the P port and A port of the first solenoid directional valve 51 are connected, and the B port and T port are connected, thereby raising the wheel chock cylinder 54. The hydraulic lock 52 is used to lock the position of the wheel chock cylinder 54, and the first double one-way throttle valve 53 is used to adjust the raising and lowering speed of the wheel chock cylinder 54.

[0063] In the embodiments of this utility model, please refer to Figure 1 and Figure 5The hydraulic control system 100 also includes a front wheel control unit 6, a rear wheel control unit 7, a front wheel lifting cylinder 78, and a rear wheel lifting cylinder 9. The front wheel control unit 6 is connected to the front wheel lifting cylinder 78 and the hydraulic oil tank 01, and the rear wheel control unit 7 is connected to the rear wheel lifting cylinder 9 and the hydraulic oil tank 01. Both the front wheel control unit 6 and the rear wheel control unit 7 include a second solenoid directional valve 61, a balance valve 62, a second double one-way throttle valve 63, and a second shut-off valve 64. When the YV6 of the second solenoid directional valve 61 is energized, the P port and B port of the second solenoid directional valve 61 are connected, and the A port and T port are connected, thereby extending the rear wheel lifting cylinder 9. When the YV7 of the second solenoid directional valve 61 is energized, the P port and A port of the second solenoid directional valve 61 are connected, and the B port and T port are connected, thereby retracting the rear wheel lifting cylinder 9. The balance valve 62 is used for locking the position of the rear wheel lifting cylinder 9, and the second double one-way throttle valve 63 is used for adjusting the rising and falling speeds of the rear wheel lifting cylinder 9. The second shut-off valve 64 is used to lower the rear wheels of the unloading machine chassis by opening it in the event of an unexpected power outage. Similarly, the operation of the front wheel control unit 6 is the same as that of the rear wheel control unit 7, and will not be described again here.

[0064] The front wheel control unit 6 and the rear wheel control unit 7 are used to control the extension and retraction of the front wheel lifting cylinder 78 and the rear wheel lifting cylinder 9, respectively, thereby driving the extension or retraction of the front and rear wheels of the mobile unloading machine chassis to switch the working state of the mobile unloading machine. Specifically, when the rear and front wheels of the mobile unloading machine chassis are extended, the mobile unloading machine can move, thereby switching the working site. When the rear and front wheels of the mobile unloading machine are retracted, the mobile unloading machine is in a fixed state and unloads vehicles.

[0065] The above description is merely an exemplary embodiment of the present utility model and does not limit the patent scope of the present utility model. Any equivalent structural transformations made based on the technical concept of the present utility model and the contents of the present utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present utility model.

Claims

1. A hydraulic control system applied to an unloading platform, the unloading platform being used for the entry or exit of an unloading machine, characterized in that, The hydraulic control system includes: The main hydraulic cylinder assembly is fixed to the side of the unloading platform near the ground and is driven to the unloading platform. The main cylinder control unit is located on the side of the main cylinder assembly closest to the ground and is connected to the main cylinder assembly and the hydraulic oil tank. A system control unit is located on the side of the main cylinder control unit closest to the ground, and is connected to the main cylinder control unit and the hydraulic oil tank; and A synchronous correction unit is located between the main cylinder control unit and the main cylinder assembly, and is connected to the main cylinder assembly and the hydraulic oil tank.

2. The hydraulic control system as described in claim 1, characterized in that, The main hydraulic cylinder assembly includes a first main hydraulic cylinder and a second main hydraulic cylinder, and the synchronous correction unit includes: Synchronous motor, wherein the oil inlet of the synchronous motor is the same as the oil inlet of the synchronous motor in the main cylinder control unit; A first piping assembly connects the synchronous motor and the first master cylinder, and the first piping assembly is equipped with a first pressure reducing valve and a first solenoid ball valve; and The second pipeline assembly connects the synchronous motor and the second main cylinder, and the second pipeline assembly is equipped with a second pressure reducing valve and a second solenoid ball valve.

3. The hydraulic control system as described in claim 2, characterized in that, The first pipeline assembly includes a first main pipe and a first branch pipe. The first main pipe is connected to the synchronous motor and the first main cylinder, and the first main pipe is connected to the hydraulic oil tank through the first branch pipe. The first pressure reducing valve and the first solenoid ball valve are both located on the first branch pipe. The second pipeline assembly includes a second main pipe and a second branch pipe. The second main pipe connects the synchronous motor and the second main cylinder, and the second main pipe is connected to the hydraulic tank through the second branch pipe. The second pressure reducing valve and the second solenoid ball valve are both located on the second branch pipe.

4. The hydraulic control system as described in claim 3, characterized in that, A first throttle valve is also provided between the first pressure reducing valve and the first solenoid ball valve. The feedback port of the first pressure reducing valve is connected to the outlet port of the first throttle valve. A second throttle valve is also provided between the second pressure reducing valve and the second solenoid ball valve. The feedback port of the second pressure reducing valve is connected to the outlet port of the second throttle valve.

5. The hydraulic control system as described in claim 3, characterized in that, The first branch pipe and the second branch pipe share a portion of the pipeline, and the synchronous correction unit further includes a third electromagnetic ball valve, which is located on the shared pipeline.

6. The hydraulic control system as described in claim 2, characterized in that, The hydraulic control system also includes an inclinometer, which is mounted on the unloading platform. The first electromagnetic ball valve and the second electromagnetic ball valve are both electrically connected to the inclinometer.

7. The hydraulic control system as described in claim 1, characterized in that, The system control unit includes a main oil circuit, a first check valve, and a solenoid relief valve. The main oil circuit is connected to the main cylinder control unit and the hydraulic oil tank. The first check valve and the solenoid relief valve are both located on the main oil circuit, and the oil inlet of the solenoid relief valve is connected to the oil outlet of the first check valve.

8. The hydraulic control system as described in claim 7, characterized in that, The system control unit also includes a third pipeline, an air cooler, and a second check valve. The third pipeline connects the hydraulic oil tank and the main oil circuit. The outlet of the electromagnetic relief valve is connected to the hydraulic oil tank through the third pipeline. The air cooler is located on the third pipeline, and the second check valve is connected in parallel with the air cooler.

9. The hydraulic control system as described in claim 8, characterized in that, The hydraulic control system also includes a wheel chock control unit and a wheel chock cylinder. The wheel chock control unit is connected to the wheel chock cylinder and the hydraulic oil tank. The wheel chock control unit includes a first solenoid directional valve, a hydraulic lock, and a first double one-way throttle valve.

10. The hydraulic control system as described in claim 1, characterized in that, The hydraulic control system further includes a front wheel control unit, a rear wheel control unit, a front wheel lifting cylinder, and a rear wheel lifting cylinder. The front wheel control unit is connected to the front wheel lifting cylinder and the hydraulic oil tank, and the rear wheel control unit is connected to the rear wheel lifting cylinder and the hydraulic oil tank. Both the front wheel control unit and the rear wheel control unit include a second electromagnetic directional valve, a balance valve, a second double one-way throttle valve, and a second shut-off valve.

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