Marine high-precision synchronous jacking hydraulic servo system

Abstract

The utility model relates to a marine high-precision synchronous jacking hydraulic servo system which comprises a jacking oil cylinder, a hydraulic oil source and a control loop. The number of the jacking oil cylinders is at least two, each jacking oil cylinder is connected with two oil ways, namely the first oil way and the second oil way, the first oil way and the second oil way are connected to the same hydraulic control one-way valve, and the hydraulic control one-way valve is further connected to an electromagnetic reversing valve through a branch; the control loop comprises an oil inlet way, an oil return way and an oil drainage way, one side of the oil inlet way, one side of the oil return way and one side of the oil drainage way are all connected into a hydraulic oil source, and the oil inlet way, the oil return way and the oil drainage way are all integrated on the same valve block. A pressure reducing valve, a pressure gauge, a pressure sensor and a plurality of proportional servo valves are sequentially arranged on the valve block, and the proportional servo valves are in one-to-one correspondence with the jacking oil cylinders. According to the hydraulic system, the barrier of traditional hydraulic control can be well solved, high-precision synchronous jacking under most working conditions can be met, the synchronous precision is high, the position precision is precise, and the principle of the hydraulic system is simple.

Description

Technical Field

[0001] This utility model relates to the field of hydraulic cylinders, and in particular to a high-precision synchronous lifting hydraulic servo system for ships. Background Technology

[0002] With the rapid development of modern industry, high-precision synchronous lifting hydraulic servo systems for special-purpose ships are being used more and more widely. Currently, existing high-precision synchronous lifting hydraulic servo systems for ships require that the main components and some parts of the hydraulic system meet the relevant standards for CCS certification. Furthermore, since ships operate on rivers or the open sea, a certain degree of tilt on the water surface needs to be considered. Traditional hydraulic systems face relatively difficult challenges in achieving high-precision control of synchronous lifting with hydraulic cylinders. Utility Model Content

[0003] The technical problem to be solved by this utility model is to provide a high-precision synchronous lifting hydraulic servo system for ships that can accurately control the actual position of the lifting cylinder in real time.

[0004] To solve the above-mentioned technical problems, the technical solution of this utility model is: a marine high-precision synchronous lifting hydraulic servo system, the innovation of which is: including a lifting cylinder, a hydraulic oil source and a control circuit;

[0005] There are at least two lifting cylinders, and each lifting cylinder is connected to two oil circuits, namely a first oil circuit and a second oil circuit. Both the first oil circuit and the second oil circuit are connected to the same hydraulic control check valve. The hydraulic control check valve is also connected to a solenoid directional valve through a branch, and the solenoid directional valve serves as the pilot oil control valve of the hydraulic control check valve.

[0006] The control circuit includes an oil inlet circuit, an oil return circuit, and an oil drain circuit. Each of the oil inlet circuit, the oil return circuit, and the oil drain circuit is connected to a hydraulic oil source on one side. A ball valve is installed on the side of the oil inlet circuit, the oil return circuit, and the oil drain circuit that is close to the hydraulic oil source. The oil inlet circuit, the oil return circuit, and the oil drain circuit are all integrated on the same valve block.

[0007] The valve block is sequentially equipped with a pressure reducing valve, a pressure gauge, a pressure sensor, and a proportional servo valve. There are several proportional servo valves, each corresponding to one of the lifting cylinders.

[0008] The oil inlet circuit is also connected to the pressure reducing valve, pressure gauge, and pressure sensor. The oil inlet circuit is equipped with oil inlet branch circuits that correspond one-to-one with each lifting cylinder. Each oil inlet branch circuit consists of two oil inlet branches, namely the first oil inlet branch and the second oil inlet branch. The first oil inlet branch is connected to a solenoid directional valve on one side, and the second oil inlet branch is connected to a proportional servo valve on one side, and then connected to a hydraulic check valve.

[0009] The return oil line is also equipped with a return oil branch group that corresponds to each lifting cylinder. The same group of return oil branch groups consists of two return oil branches, namely the first return oil branch and the second return oil branch. One side of the first return oil branch is connected to the solenoid directional valve, and one side of the second return oil branch is connected to the proportional servo valve and then to the hydraulic control check valve.

[0010] The hydraulic oil source supplies hydraulic oil to the valve block. After being depressurized by the pressure reducing valve, the hydraulic oil is supplied to the lifting cylinder. The oil in the pressure reducing valve drain circuit flows back to the hydraulic oil source.

[0011] Furthermore, a safety branch is provided on the second oil line of the lifting cylinder, and a safety valve is provided on the safety branch.

[0012] Furthermore, a magnetostrictive displacement sensor is also installed on the lifting cylinder.

[0013] The advantages of this utility model are as follows: In this utility model, the hydraulic power is mainly provided by the hydraulic oil source, and the control valve group adopts a high linearity zero-coverage servo proportional valve group, and is combined with a proportional servo with good linearity, which can effectively solve the barriers of traditional hydraulic control. This hydraulic system can meet the high-precision synchronous lifting requirements under most working conditions, with high synchronization accuracy, accurate position accuracy, and simple hydraulic system principle.

[0014] The magnetostrictive displacement sensor installed on the lifting cylinder is used with a motion controller to precisely control the servo valve group, which can achieve real-time and precise control of the actual position of the lifting cylinder.

[0015] The hydraulic servo system of this invention can optimize the valve control of traditional hydraulic systems to a great extent, making the hydraulic system simpler and more intuitive. It can effectively avoid the internal leakage of some valves and the potential risks of too many joints and pipelines. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the high-precision synchronous lifting hydraulic servo system for ships according to this utility model. Detailed Implementation

[0017] To further illustrate the technical means and effects adopted by this utility model in order to achieve the intended utility model purpose, the following detailed description of the specific implementation methods, structure, features and effects of this utility model is provided in conjunction with the accompanying drawings and preferred embodiments.

[0018] like Figure 1 The above describes a high-precision synchronous lifting hydraulic servo system for marine applications, which includes a lifting cylinder 2, a hydraulic oil source 1, and a control circuit. The hydraulic oil source 1 must meet the relevant CCS marine standards.

[0019] There are at least two lifting cylinders 2, and each lifting cylinder 2 is connected to two oil circuits, namely a first oil circuit 21 and a second oil circuit 22. Both the first oil circuit 21 and the second oil circuit 22 are connected to the same hydraulic control check valve 24. The hydraulic control check valve 24 is also connected to a solenoid directional valve 26 through a branch circuit 25. The solenoid directional valve 26 serves as the pilot oil control valve for the hydraulic control check valve 24. The pilot oil circuit is switched by the solenoid directional valve 26 to open and close the hydraulic control check valve 24. In this embodiment, there are two lifting cylinders 2, and each lifting cylinder 2 is also equipped with a magnetostrictive displacement sensor 23. For the magnetostrictive displacement sensor 23 installed on the lifting cylinder 2, a motion controller is used to precisely control the servo valve group, which can achieve real-time precise control of the actual precise position of the lifting cylinder 2.

[0020] The control circuit includes an oil inlet line 3, an oil return line 4, and an oil drain line 5. One side of each of the oil inlet line 3, the oil return line 4, and the oil drain line 5 is connected to a hydraulic oil source 1. A ball valve 7 is installed on the side of each of the oil inlet line 3, the oil return line 4, and the oil drain line 5 that is close to the hydraulic oil source 1. The hydraulic oil source 1 is also provided with an oil inlet, an oil return, and an oil drain corresponding to the oil inlet line 3, the oil return line 4, and the oil drain line 5. All of these are integrated on the same valve block 6.

[0021] A pressure reducing valve 7, a pressure gauge 8, a pressure sensor 9, and a proportional servo valve 10 are sequentially arranged on the valve block 6. There are two proportional servo valves 10, which correspond one-to-one with the two lifting cylinders 2.

[0022] The oil inlet line 3 is also connected to the pressure reducing valve 7, pressure gauge 8, and pressure sensor 9. The oil inlet line 3 is also equipped with an oil inlet branch group that is connected to the two lifting cylinders 2 in a one-to-one manner. The same oil inlet branch group consists of two oil inlet branches, namely the first oil inlet branch 11 and the second oil inlet branch 12. The first oil inlet branch 11 is connected to the solenoid directional valve 26 on one side, and the second oil inlet branch 12 is connected to the proportional servo valve 10 on one side, and then connected to the hydraulic check valve 24, and finally connected to the first oil line 21.

[0023] On the return oil line 4, there is also a return oil branch group that is connected to the two lifting cylinders 2 one by one. The same group of return oil branches consists of two return oil branches, namely the first return oil branch 13 and the second return oil branch 14. One side of the first return oil branch 13 is connected to the solenoid directional valve 26, and one side of the second return oil branch 14 is connected to the proportional servo valve 10, then connected to the hydraulic check valve 24, and finally connected to the second oil line 22.

[0024] A pressure reducing valve 7 is connected to the oil supply line of valve block 6. The pressure-reduced hydraulic oil enters the solenoid directional valve 26, the hydraulic control check valve 24, and the proportional servo valve 10. At the same time, the oil leaking from the pressure reducing valve 7 flows back to the hydraulic oil source 1 through the drain line on valve block 6.

[0025] A safety branch 27 is also provided on the second oil circuit 22 of the lifting cylinder 2, and a safety valve 28 is provided on the safety branch 27.

[0026] This utility model discloses a high-precision synchronous lifting hydraulic servo system for ships, used in a synchronous lifting system with multiple sets of hydraulic cylinders within a certain flow range. Figure 1 The principle shown is only for the synchronizing of the lifting of two lifting cylinders 2. If it is a multi-cylinder synchronization, the corresponding control valve group and corresponding oil passage can be added according to the principle.

[0027] In this utility model's marine high-precision synchronous lifting hydraulic servo system, the entire system's oil supply pressure is determined by the hydraulic oil source 1. Therefore, to adapt to different working conditions, the pressure reducing valve 7 can be adjusted to the pressure of the actuator. The pressure gauge 8 and pressure sensor 9 can intuitively read and the display screen can collect pressure values. The proportional servo valve 10 changes the running speed of the lifting cylinder 2 according to the working conditions. The magnetostrictive displacement sensor 23 can provide real-time feedback on the lifting height of the lifting cylinder 2. Through the position parameters fed back by the magnetostrictive displacement sensor 23 and the position closed-loop control of the motion controller, the lifting positions of the two lifting cylinders 2 can be adjusted in real time to achieve synchronous lifting. The hydraulic control check valve can provide pilot oil through the solenoid directional valve 26 when the cylinder needs to be stopped according to the electrical control command, allowing the cylinder to be stopped and locked at any position. At the same time, considering that if a fault occurs in the rod chamber during the lifting process of the lifting cylinder 2, the pressure may be too high, leading to overshoot and accidents, a safety valve 28 is set at the rodless chamber end of the lifting cylinder to limit the maximum pressure, ensuring the safety and reliability of the entire system.

[0028] The hydraulic servo system of this invention can optimize the valve control of traditional hydraulic systems to a great extent, making the hydraulic system simpler and more intuitive. It can effectively avoid the internal leakage of some valves and the potential risks of too many joints and pipelines.

[0029] The system achieves simultaneous displacement accuracy of ±0.001mm, with rapid response speed, enabling quick and accurate fulfillment of the cylinder's movement and position requirements. In the event of a power outage or cessation of operation, the servo valve remains in the neutral position, effectively locking the cylinder and preventing further incidents.

[0030] Since marine equipment is used on water, the entire equipment structure may be affected by water flow, resulting in a certain degree of tilting and a certain degree of off-center loading of the mechanical structure. During the lifting process, the lifting cylinder 2 will experience tilting force. If conventional hydraulic control is used, the lifting cylinder 2 may have a displacement difference when it reaches the required synchronization time. However, this utility model adopts servo synchronous control and can use flow compensation to adjust the individual operating speed of each lifting cylinder 2, thereby realizing the synchronous lifting process of the lifting cylinder 2.

[0031] The above description is merely a preferred embodiment of the present utility model and is not intended to limit the present utility model in any way. Although the present utility model has been disclosed above with reference to a preferred embodiment, it is not intended to limit the present utility model. Any person skilled in the art can make some modifications or alterations to the above-disclosed technical content to create equivalent embodiments without departing from the scope of the present utility model. Any simple modifications, equivalent changes and alterations made to the above embodiments based on the technical essence of the present utility model without departing from the scope of the present utility model shall still fall within the scope of the present utility model.

Claims

1. A high-precision synchronous lifting hydraulic servo system for ships, characterized in that: This includes the lifting cylinder, hydraulic oil source, and control circuit; There are at least two lifting cylinders, and each lifting cylinder is connected to two oil circuits, namely a first oil circuit and a second oil circuit. Both the first oil circuit and the second oil circuit are connected to the same hydraulic control check valve. The hydraulic control check valve is also connected to a solenoid directional valve through a branch, and the solenoid directional valve serves as the pilot oil control valve of the hydraulic control check valve. The control circuit includes an oil inlet circuit, an oil return circuit, and an oil drain circuit. Each of the oil inlet circuit, the oil return circuit, and the oil drain circuit is connected to a hydraulic oil source on one side. A ball valve is installed on the side of the oil inlet circuit, the oil return circuit, and the oil drain circuit that is close to the hydraulic oil source. The oil inlet circuit, the oil return circuit, and the oil drain circuit are all integrated on the same valve block. The valve block is sequentially equipped with a pressure reducing valve, a pressure gauge, a pressure sensor, and a proportional servo valve. There are several proportional servo valves, each corresponding to one of the lifting cylinders. The oil inlet circuit is also connected to the pressure reducing valve, pressure gauge, and pressure sensor. The oil inlet circuit is equipped with oil inlet branch circuits that correspond one-to-one with each lifting cylinder. Each oil inlet branch circuit consists of two oil inlet branches, namely the first oil inlet branch and the second oil inlet branch. The first oil inlet branch is connected to a solenoid directional valve on one side, and the second oil inlet branch is connected to a proportional servo valve on one side, and then connected to a hydraulic check valve. The return oil line is also equipped with a return oil branch group that corresponds to each lifting cylinder. The same group of return oil branch groups consists of two return oil branches, namely the first return oil branch and the second return oil branch. One side of the first return oil branch is connected to the solenoid directional valve, and one side of the second return oil branch is connected to the proportional servo valve and then to the hydraulic control check valve. The hydraulic oil source supplies hydraulic oil to the valve block. After the pressure is reduced by the pressure reducing valve, the hydraulic oil is supplied to the lifting cylinder. The oil in the pressure reducing valve drain circuit flows back to the hydraulic oil source.

2. The marine high-precision synchronous lifting hydraulic servo system according to claim 1, characterized in that: A safety branch is also provided on the second oil line of the lifting cylinder, and a safety valve is installed on the safety branch.

3. The marine high-precision synchronous lifting hydraulic servo system according to claim 1, characterized in that: The lifting cylinder is also equipped with a magnetostrictive displacement sensor.

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