A riser suspension hydraulic control system

Abstract

A riser suspension hydraulic control system, the riser suspension hydraulic control system includes an oil tank, a check valve, a hydraulic pump set, a high-pressure check valve, a first main control valve group, a second main control valve group, a third main control valve group, a lateral support cylinder group, an upper cone cylinder, and a lock rod cylinder group; the oil outlet end of the oil tank is communicated with the oil inlet end of the hydraulic pump set, the oil outlet end of the hydraulic pump set is communicated with the oil inlet end of the pressure oil filter, the oil outlet end of the pressure oil filter is communicated with the oil inlet end of the high-pressure check valve, the oil outlet end of the high-pressure check valve is communicated with the oil inlet end P2-1 of the first main control valve group, and a pressure reducing valve is arranged between the oil circuit of the high-pressure check valve and the first main control valve group. This design can control the moving speed of the piston in the hydraulic cylinder when it works, making the hydraulic system have strong stability. At the same time, it can limit the maximum flow rate into the hydraulic cylinder, thereby preventing the piston from moving too fast and damaging the seals, and extending the working life of the hydraulic cylinder.

Description

Technical Field

[0001] The invention relates to an improvement of a riser hydraulic system technology, belongs to the field of multi-point mooring FPSO hydraulic systems, and in particular to a riser suspension hydraulic control system. Background Art

[0002] With the growing demand for oil and gas resources, the pace of offshore oil and gas development is also accelerating, and the deep sea has become the focus of offshore oil and gas development. As an important part of the deep-sea oil and gas field development system structure, risers can be roughly divided into four categories: 1) top pre-tensioned risers; 2) steel catenary risers; 3) flexible risers; 4) tower risers. Compared with shallow water riser technology, deep water riser technology faces more severe environmental challenges such as water depth, high pressure, and low temperature.

[0003] The existing riser hydraulic system mainly includes control components such as variable pump, safety valve, flow control valve, etc. The variable pump outputs a certain flow of hydraulic oil to drive the piston in the hydraulic cylinder to move, and the reversing valve and flow control valve control the movement speed and direction of the piston in the hydraulic cylinder, thereby achieving axial positioning and axial locking of the riser. The existing riser hydraulic system mainly has the following problems: poor stability of the hydraulic system, short service life of the hydraulic cylinder, and uncontrollable temperature of the hydraulic oil.

[0004] A Chinese patent application with application number CN201810318436.3 and application date April 11, 2018 discloses a dynamic test bench oil supply and return hydraulic circulation system, which is implemented by the following technical scheme: adding continuous flushing of oil at the oil inlet and outlet of the tested product to form an oil return pipeline for continuous heat exchange; connecting the rodless chamber oil return needle valve 13, the rodless chamber two-position two-way solenoid valve 14 and the rod chamber two-position two-way solenoid valve 15 in series between the rodless chamber inlet of the tested product and the oil return pipeline, The rod chamber return oil needle valve 12 and the two-position three-way solenoid reversing valve 11 and the three-position three-way reversing valve 10 together control the return oil circuit circulation, and the discharged oil flows directly back to the oil tank through the two-position three-way solenoid reversing valve; the oil temperature at the inlet of the test product is detected, and the oil temperature of the test product and the oil circulation circuit of continuous flushing and continuous heat exchange are automatically controlled through the test bench temperature control system. Although the oil temperature is controlled in this patent, the problems of poor stability of the hydraulic system and short working life of the hydraulic cylinder are still not solved.

[0005] The information disclosed in this background technology section is only intended to increase the understanding of the overall background of this patent application, and should not be regarded as acknowledging or suggesting in any form that the information constitutes the prior art already known to ordinary technicians in this field. Summary of the invention

[0006] The object of the present invention is to overcome the problems in the prior art that the stability of the hydraulic system is poor and the working life of the hydraulic cylinder is short, and to provide a riser suspension hydraulic control system with strong stability of the hydraulic system and long working life of the hydraulic cylinder.

[0007] To achieve the above object, the technical solution of the present invention is: a riser suspension hydraulic control system, which includes an oil tank, a one-way valve, a hydraulic pump unit, a high-pressure one-way valve, a first main control valve group, a second main control valve group, a third main control valve group, a lateral support cylinder group, an upper cone cylinder, and a locking rod cylinder group;

[0008] The oil outlet end of the oil tank is connected to the oil inlet end of the hydraulic pump unit, the oil outlet end of the hydraulic pump unit is connected to the oil inlet end of the pressure oil filter, the oil outlet end of the pressure oil filter is connected to the oil inlet end of the high-pressure one-way valve, the oil outlet end of the high-pressure one-way valve is connected to the oil inlet end P2-1 of the first main control valve group, a pressure reducing valve is arranged between the oil path of the high-pressure one-way valve and the first main control valve group, the oil outlet end of the high-pressure one-way valve is connected to the oil inlet end of the second main control valve group, the oil outlet end of the high-pressure one-way valve is connected to the oil inlet end of the third main control valve group, a heating valve group is arranged between the oil path of the high-pressure one-way valve and the third main control valve group, the oil outlet end of the first main control valve group is connected to the oil inlet end of the lateral support cylinder group through an umbilical cable, the oil outlet end of the second main control valve group is connected to the oil inlet end of the upper cone cylinder through an umbilical cable, and the oil outlet end of the third main control valve group is connected to the oil inlet end of the locking rod cylinder group through an umbilical cable;

[0009] The structures of the first main control valve group, the second main control valve group, and the third main control valve group are the same;

[0010] The first main control valve group includes a flow control valve, a first throttle stop valve, a three-position four-way electromagnetic reversing valve, and a balance valve. The oil inlet end of the flow control valve is connected to the oil outlet end of the high-pressure one-way valve through the P2-1 port, the oil outlet end of the flow control valve is connected to the oil inlet end of the first throttle stop valve, the oil outlet end of the first throttle stop valve is connected to the oil inlet end of the three-position four-way electromagnetic reversing valve through a hose, the oil outlet end of the three-position four-way electromagnetic reversing valve is connected to the oil inlet end of the balance valve, and the oil outlet end of the balance valve is connected to the oil inlet end of the lateral support cylinder group;

[0011] The oil inlet end of the oil tank is connected to the oil outlet end of a return oil filter, the oil inlet end of the return oil filter is connected to the oil outlet end of the one-way valve, the oil inlet end of the one-way valve is connected to the oil outlet end T- of the first main control valve group, the oil inlet end of the one-way valve is connected to the oil outlet end of the second main control valve group, and the oil inlet end of the one-way valve is connected to the oil outlet end of the third main control valve group.

[0012] The oil inlet end of the oil tank is connected to the oil outlet end of a second return oil filter, and the oil inlet end of the second return oil filter is connected to the oil outlet end of the one-way valve.

[0013] An oil cooler is provided on the oil path between the first oil return filter and the one-way valve, and also on the oil path between the second oil return filter and the one-way valve.

[0014] A thermometer, an air filter, and a temperature sensor are sequentially provided on the fuel tank.

[0015] Pressure sensors are provided on the oil paths between the high-pressure one-way valve and the first main control valve group, between the high-pressure one-way valve and the second main control valve group, and between the high-pressure one-way valve and the third main control valve group. The oil path between the high-pressure one-way valve and the pressure sensor is connected to the inlet end of the safety valve, and the outlet end of the safety valve is connected to the inlet end of the fuel tank.

[0016] The outlet end of the first throttle stop valve is connected to the inlet port P of the three-position four-way electromagnetic directional valve through a hose. The working port A of the three-position four-way electromagnetic directional valve is connected to the left free port of the balance valve, and the working port B of the three-position four-way electromagnetic directional valve is connected to the right free port of the balance valve. The left load port of the balance valve is connected to the inlet end of the transverse support cylinder group, and the right load port of the balance valve is connected to the inlet end of the transverse support cylinder group. The return port T of the three-position four-way electromagnetic directional valve is connected to the inlet end of the one-way valve through the T2-1 port of the first main control valve group.

[0017] A second throttle stop valve and a relief valve are sequentially provided between the inlet pipeline and the outlet pipeline of the first main control valve group. A main control one-way valve is provided on the balance valve, and a protection one-way valve is provided on the return oil path of the return port T of the three-position four-way electromagnetic directional valve.

[0018] The transverse support cylinder group includes a plurality of support cylinders. The rodless chambers of all the support cylinders are connected to the left load port of the balance valve, and the rod chambers of all the support cylinders are connected to the right load port of the balance valve.

[0019] The heating valve group includes a heating stop valve and a throttle orifice. The outlet end of the high-pressure one-way valve is connected to the inlet end of the heating stop valve through the P port. The outlet end of the heating stop valve is connected to the inlet end of the throttle orifice, and the outlet end of the throttle orifice is connected to the inlet end of the third main control valve group through the T port.

[0020] A first heating one-way valve is provided on the oil path at the inlet end of the heating stop valve, and a second heating one-way valve is provided on the oil path at the outlet end of the throttle orifice.

[0021] Compared with the prior art, the beneficial effects of the present invention are:

[0022] 1. In a riser suspension hydraulic control system of the present invention, the oil outlet end of the oil tank is connected to the oil inlet end of the hydraulic pump set, the oil outlet end of the hydraulic pump set is connected to the oil inlet end of the pressure oil filter, the oil outlet end of the pressure oil filter is connected to the oil inlet end of the high-pressure check valve, the oil outlet end of the high-pressure check valve is connected to the oil inlet end P- of a main control valve group. A pressure reducing valve is provided between the oil path of the high-pressure check valve and the main control valve group. The pressure reducing valve reduces the pressure of the hydraulic oil flowing through the second and third main control valve groups. The oil outlet end of the high-pressure check valve is connected to the oil inlet end of the second main control valve group and the oil inlet end of the third main control valve group. A heating valve group is provided between the oil path of the high-pressure check valve and the third main control valve group. The oil outlet end of the first main control valve group is connected to the oil inlet end of the transverse support cylinder group through an umbilical cable. After starting the hydraulic pump set, the hydraulic pump set sucks oil from the oil tank through the oil suction port, and the output pressure oil enters the main oil inlet pipe through the pressure oil filter and the high-pressure check valve. The hydraulic oil in the main circuit enters the main oil return pipe after passing through the heating valve group, and finally returns to the oil tank after passing through the check valve and the oil return filter. In the hydraulic oil branch circuit, the movement speed of the piston in the transverse support cylinder group is controlled by the first main control valve group. The hydraulic oil directly overflows into the main oil return pipe through the first main control valve group and returns to the oil tank. The first main control valve group controls the movement direction of the piston in the transverse support cylinder group. A flow control valve is provided at the oil inlet of each hydraulic cylinder, which can control the movement speed of the piston when the hydraulic cylinder works, making the hydraulic system more stable. At the same time, it can limit the maximum flow rate into the hydraulic cylinder, thereby preventing the piston from moving too fast and damaging the seals, and extending the service life of the hydraulic cylinder. Therefore, this design has strong stability and a long service life.

[0023] 2. In a riser suspension hydraulic control system of the present invention, the oil path between the high-pressure check valve and the pressure sensor is connected to the oil inlet end of the safety valve. The pressure sensor real-time feedbacks the pressure of the hydraulic oil on the main oil inlet path. The oil outlet end of the safety valve is connected to the oil inlet end of the oil tank. It mainly plays a pressure limiting and protecting role in the hydraulic system to prevent danger caused by excessive pressure in the main oil inlet path of the hydraulic system. A protection check valve is provided on the oil return path of the oil return port T of the three-position four-way electromagnetic reversing valve. The balance valve realizes the smooth operation of the transverse support cylinder group. A protection check valve is provided at the outlet of the oil return path of the three-position four-way electromagnetic reversing valve to prevent seawater from pouring into the oil return pipe under pressure and eroding and damaging relatively precise valve parts such as the three-position four-way electromagnetic reversing valve and the balance valve when the main oil return pipe ruptures. Therefore, this design has high safety and stable use.

[0024] 3. In a vertical pipe suspension hydraulic control system of the present invention, the heating valve group includes a heating stop valve and a throttle orifice. The oil outlet end of the high-pressure check valve is connected to the oil inlet end of the heating stop valve through port P. The oil outlet end of the heating stop valve is connected to the oil inlet end of the throttle orifice. The oil outlet end of the throttle orifice is connected to the oil inlet end of the three main control valve groups through port T. A heating check valve is provided on the oil inlet end oil path of the heating stop valve, and a second heating check valve is provided on the oil outlet end oil path of the throttle orifice. The horizontal support cylinder group realizes the axial positioning of the rigid riser, the upper cone cylinder realizes the axial locking of the rigid riser, and the lock rod cylinder group realizes the axial locking of the flexible riser. Therefore, this design can control the temperature of the oil and the working environment is stable. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 is a schematic structural diagram of the present invention.

[0026] Figure 2 is a schematic diagram of the oil circuit connection of the fuel tank in the present invention.

[0027] Figure 3 is a schematic structural diagram of a main control valve group in the present invention.

[0028] Figure 4 is a schematic structural diagram of the heating valve group in the present invention.

[0029] Figure 5 is a schematic diagram of the connection between a main control valve group and the horizontal support cylinder group in the present invention.

[0030] In the figure: thermometer 1, fuel tank 2, first oil return filter 3, second oil return filter 3.1, air cooler 4, check valve 5, hydraulic pump group 6, pressure oil filter 7, high-pressure check valve 8, pressure sensor 9, safety valve 10, first main control valve group 11, flow control valve 111, first throttle stop valve 112, second throttle stop valve 113, overflow valve 114, hose 115, three-position four-way electromagnetic directional control valve 116, main control check valve 117, balance valve 118, protective check valve 119, left load port 1181, left free port 1182, right load port 1183, right free port 1184, second main control valve group 11.1, third main control valve group 11.2, pressure reducing valve 12, heating valve group 13, first heating check valve 131, heating stop valve 132, throttle orifice 133, second heating check valve 134, umbilical cable 14, horizontal support cylinder group 15, support cylinder 151, upper cone cylinder 16, lock rod cylinder group 17, air filter 18, temperature sensor 19. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0031] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0032] See Figures 1 to 5, a riser suspension hydraulic control system, which includes an oil tank 2, a one-way valve 5, a hydraulic pump unit 6, a high-pressure one-way valve 8, a first main control valve group 11, a second main control valve group 11.1, a third main control valve group 11.2, a lateral support cylinder group 15, an upper cone cylinder 16, and a locking rod cylinder group 17;

[0033] The oil outlet end of the oil tank 2 is connected to the oil inlet end of the hydraulic pump unit 6, the oil outlet end of the hydraulic pump unit 6 is connected to the oil inlet end of the pressure oil filter 7, the oil outlet end of the pressure oil filter 7 is connected to the oil inlet end of the high-pressure one-way valve 8, the oil outlet end of the high-pressure one-way valve 8 is connected to the oil inlet end P2-1 of the first main control valve group 11. A pressure reducing valve 12 is arranged between the oil circuit of the high-pressure one-way valve 8 and the first main control valve group 11. The oil outlet end of the high-pressure one-way valve 8 is connected to the oil inlet end of the second main control valve group 11.1, and the oil outlet end of the high-pressure one-way valve 8 is connected to the oil inlet end of the third main control valve group 11.2. A heating valve group 13 is arranged between the oil circuit of the high-pressure one-way valve 8 and the third main control valve group 11.2. The oil outlet end of the first main control valve group 11 is connected to the oil inlet end of the lateral support cylinder group 15 through an umbilical cable 14, the oil outlet end of the second main control valve group 11.1 is connected to the oil inlet end of the upper cone cylinder 16 through the umbilical cable 14, and the oil outlet end of the third main control valve group 11.2 is connected to the oil inlet end of the locking rod cylinder group 17 through the umbilical cable 14;

[0034] The structures of the first main control valve group 11, the second main control valve group 11.1, and the third main control valve group 11.2 are the same;

[0035] The first main control valve group 11 includes a flow control valve 111, a first throttle stop valve 112, a three-position four-way electromagnetic directional control valve 116, and a balance valve 118. The oil inlet end of the flow control valve 111 is connected to the oil outlet end of the high-pressure one-way valve 8 through the P2-1 port. The oil outlet end of the flow control valve 111 is connected to the oil inlet end of the first throttle stop valve 112. The oil outlet end of the first throttle stop valve 112 is connected to the oil inlet end of the three-position four-way electromagnetic directional control valve 116 through a hose 115. The oil outlet end of the three-position four-way electromagnetic directional control valve 116 is connected to the oil inlet end of the balance valve 118. The oil outlet end of the balance valve 118 is connected to the oil inlet end of the lateral support cylinder group 15;

[0036] The oil inlet end of the oil tank 2 is connected to the oil outlet end of a return oil filter 3. The oil inlet end of the return oil filter 3 is connected to the oil outlet end of the one-way valve 5. The oil inlet end of the one-way valve 5 is connected to the oil outlet end T2-1 of the first main control valve group 11, the oil inlet end of the one-way valve 5 is connected to the oil outlet end of the second main control valve group 11.1, and the oil inlet end of the one-way valve 5 is connected to the oil outlet end of the third main control valve group 11.2.

[0037] The oil inlet end of the oil tank 2 is connected to the oil outlet end of a second return oil filter 3.1. The oil inlet end of the second return oil filter 3.1 is connected to the oil outlet end of the one-way valve 5.

[0038] An oil cooler 4 is provided on the oil circuits between the first oil return filter 3 and the check valve 5, and between the second oil return filter 3.1 and the check valve 5.

[0039] A thermometer 1, an air filter 18, and a temperature sensor 19 are sequentially provided on the fuel tank 2.

[0040] Pressure sensors 9 are provided on the oil circuits between the high-pressure check valve 8 and the first main control valve group 11, between the high-pressure check valve 8 and the second main control valve group 11.1, and between the high-pressure check valve 8 and the third main control valve group 11.2. The oil circuit between the high-pressure check valve 8 and the pressure sensor 9 is connected to the inlet end of the safety valve 10, and the outlet end of the safety valve 10 is connected to the inlet end of the fuel tank 2.

[0041] The outlet end of the first throttle stop valve 112 is connected to the inlet port P of the three-position four-way solenoid directional control valve 116 through a hose 115. The working port A of the three-position four-way solenoid directional control valve 116 is connected to the left free port 1182 of the balance valve 118, and the working port B of the three-position four-way solenoid directional control valve 116 is connected to the right free port 1184 of the balance valve 118. The left load port 1181 of the balance valve 118 is connected to the inlet end of the transverse support cylinder group 15, and the right load port 1183 of the balance valve 118 is connected to the inlet end of the transverse support cylinder group 15. The return port T of the three-position four-way solenoid directional control valve 116 is connected to the inlet end of the check valve 5 through the T2-1 port of the first main control valve group 11.

[0042] A second throttle stop valve 113 and a relief valve 114 are sequentially provided between the inlet pipeline and the outlet pipeline of the first main control valve group 11. A main control check valve 117 is provided on the balance valve 118, and a protection check valve 119 is provided on the return oil path of the return port T of the three-position four-way solenoid directional control valve 116.

[0043] The transverse support cylinder group 15 includes a plurality of support cylinders 151. The rodless chambers of all the support cylinders 151 are connected to the left load port 1181 of the balance valve 118, and the rod chambers of all the support cylinders 151 are connected to the right load port 1183 of the balance valve 118.

[0044] The heating valve group 13 includes a heating stop valve 132 and a throttle orifice 133. The outlet end of the high-pressure check valve 8 is connected to the inlet end of the heating stop valve 132 through the P5 port. The outlet end of the heating stop valve 132 is connected to the inlet end of the throttle orifice 133, and the outlet end of the throttle orifice 133 is connected to the inlet end of the third main control valve group 11.2 through the T5 port.

[0045] A first heating check valve 131 is provided on the oil path at the inlet end of the heating stop valve 132, and a second heating check valve 134 is provided on the oil path at the outlet end of the throttle orifice 133.

[0046] The principle of the present invention is described as follows: After starting the hydraulic pump unit 6, the hydraulic pump unit 6 sucks oil from the oil tank 2 through the oil suction port, and the output pressurized oil enters the main oil inlet pipe through the oil pressure filter 7, the high-pressure check valve 8, and the pressure sensor 9. In the main circuit, the hydraulic oil enters the main oil return pipe after passing through the heating valve group 13, and finally returns to the oil tank 2 after passing through the check valve 5, the air cooler 4, and the oil return filter 3. In the hydraulic oil branch, the movement speed of the piston in the horizontal support cylinder group 15 is controlled by the flow control valve 111, the throttle stop valve 112, and the second throttle stop valve 113 in the main control valve group 11. The flow control valve 111 controls the on-off of the oil inlet branch pipe and the main oil return pipe. The overflow valve 114 protects the horizontal support cylinder group 15. When the pressure exceeds the set pressure value of the overflow valve 114, the hydraulic oil directly overflows through the overflow valve 114 into the main oil return pipe and returns to the oil tank 2. The three-position four-way electromagnetic reversing valve 116 controls the movement direction of the piston in the horizontal support cylinder group 15. When the electromagnet DT1 is energized and DT2 is de-energized, the left position of the three-position four-way electromagnetic reversing valve 116 is connected, and the piston rod in the horizontal support cylinder group 15 retracts. When the electromagnet DT2 is energized and DT1 is de-energized, the right position of the three-position four-way electromagnetic reversing valve 116 is connected, and the piston rod in the horizontal support cylinder group 15 extends. The balance valve 118 realizes the smooth operation of the horizontal support cylinder group 15 and can stop at any position. The control principle of the main control valve group 11.1 for the upper cone cylinder 16 and the control principle of the main control valve group 11.2 for the locking rod cylinder group 17 are the same as the control principle of the main control valve group 11 for the horizontal support cylinder group 15.

[0047] When the temperature of the hydraulic oil is relatively low, the viscosity of the hydraulic oil in the pipeline is relatively large, which is not conducive to the good operation of the hydraulic system. When the temperature of the hydraulic oil is too high, it will accelerate the evaporation of water in the water-glycol hydraulic oil. When the water content in the water-glycol hydraulic oil is less than 35%, its fire resistance will be greatly reduced and the viscosity of the hydraulic oil will increase significantly. The optimal working temperature of the water-glycol hydraulic oil is +40°C to +50°C (taking N46-water glycol as an example). In the hydraulic system, the temperature sensor 19 real-time feedbacks the temperature of the hydraulic oil in the oil tank 2, and the temperature of the hydraulic oil in the hydraulic system is controlled within its optimal working range through the air cooler 4 and the heating valve group 13, so that the hydraulic system operates better. When the temperature of the hydraulic oil is relatively low, the heating stop valve 132 in the heating valve group 13 is opened to connect the main oil inlet pipe and the main oil return pipe in the hydraulic system, and the hydraulic oil in the hydraulic pipeline can be circulated and heated through the throttle orifice 133 of the heating valve group 13. When the temperature of the hydraulic oil is relatively high, the air cooler 4 is turned on to cool the hydraulic oil in the pipeline, so that the hydraulic oil in the hydraulic system operates at the optimal temperature.

[0048] Example 1:

[0049] A riser suspension hydraulic control system, which includes an oil tank 2, a check valve 5, a hydraulic pump unit 6, a high-pressure check valve 8, a first main control valve group 11, a second main control valve group 11.1, a third main control valve group 11.2, a lateral support oil cylinder group 15, an upper cone oil cylinder 16, and a lock rod oil cylinder group 17; the oil outlet end of the oil tank 2 is communicated with the oil inlet end of the hydraulic pump unit 6, the oil outlet end of the hydraulic pump unit 6 is communicated with the oil inlet end of an oil pressure filter 7, the oil outlet end of the oil pressure filter 7 is communicated with the oil inlet end of the high-pressure check valve 8, the oil outlet end of the high-pressure check valve 8 is communicated with the oil inlet end P2-1 of the first main control valve group 11, a pressure reducing valve 12 is arranged between the oil path of the high-pressure check valve 8 and the first main control valve group 11, and the pressure reducing valve 12 reduces the pressure of the hydraulic oil flowing through the second main control valve group 11.1 and the third main control valve group 11.2; the oil outlet end of the high-pressure check valve 8 is communicated with the oil inlet end of the second main control valve group 11.1, the oil outlet end of the high-pressure check valve 8 is communicated with the oil inlet end of the third main control valve group 11.2, and a heating valve group 13 is arranged between the oil path of the high-pressure check valve 8 and the third main control valve group 11.2; the oil outlet end of the first main control valve group 11 is communicated with the oil inlet end of the lateral support oil cylinder group 15 through an umbilical cable 14, the oil outlet end of the second main control valve group 11.1 is communicated with the oil inlet end of the upper cone oil cylinder 16 through the umbilical cable 14, the oil outlet end of the third main control valve group 11.2 is communicated with the oil inlet end of the lock rod oil cylinder group 17 through the umbilical cable 14, and hydraulic pipelines, electrical circuits, etc. are integrated in the umbilical cable 14; the first main control valve group 11, the second main control valve group 11.1, and the third main control valve group 11.2 have the same structure; the first main control valve group 11 includes a flow control valve 111, a first throttle stop valve 112, a three-position four-way electromagnetic directional control valve 116, and a balance valve 118. The oil inlet end of the flow control valve 111 is communicated with the oil outlet end of the high-pressure check valve 8 through the P2-1 port, the oil outlet end of the flow control valve 111 is communicated with the oil inlet end of the first throttle stop valve 112, the oil outlet end of the first throttle stop valve 112 is communicated with the oil inlet end of the three-position four-way electromagnetic directional control valve 116 through a hose 115, the oil outlet end of the three-position four-way electromagnetic directional control valve 116 is communicated with the oil inlet end of the balance valve 118, and the oil outlet end of the balance valve 118 is communicated with the oil inlet end of the lateral support oil cylinder group 15; the oil inlet end of the oil tank 2 is communicated with the oil outlet end of a return oil filter 3, the oil inlet end of the return oil filter 3 is communicated with the oil outlet end of the check valve 5, the oil inlet end of the check valve 5 is communicated with the oil outlet end T2-1 of the first main control valve group 11, the oil inlet end of the check valve 5 is communicated with the oil outlet end of the second main control valve group 11.1, and the oil inlet end of the check valve 5 is communicated with the oil outlet end of the third main control valve group 11.2.

[0050] During application: After starting the hydraulic pump unit 6, the oil outlet end of the oil tank 2 is connected to the oil inlet end of the hydraulic pump unit 6, the oil outlet end of the hydraulic pump unit 6 is connected to the oil inlet end of the pressure oil filter 7, the oil outlet end of the pressure oil filter 7 is connected to the oil inlet end of the high-pressure check valve 8 and enters a main control valve group 11, a second main control valve group 11.1, and a third main control valve group 11.2. The oil outlet end of the high-pressure check valve 8 is connected to the oil inlet end of the flow control valve 111, the oil outlet end of the flow control valve 111 is connected to the oil inlet end of a throttle stop valve 112, the oil outlet end of the throttle stop valve 112 is connected to the oil inlet end of a three-position four-way electromagnetic reversing valve 116 through a hose 115, the oil outlet end of the three-position four-way electromagnetic reversing valve 116 is connected to the oil inlet end of a balance valve 118, and the oil outlet end of the balance valve 118 is connected to the oil inlet end of the transverse support cylinder group 15. The main control valve group 11, the second main control valve group 11.1, and the third main control valve group 11.2 enter the main return pipe after passing through the heating valve group 13, and finally return to the oil tank 2 after passing through the check valve 5 and the return oil filter 3. In the hydraulic oil branch, the movement speed of the piston in the transverse support cylinder group 15 is controlled by the main control valve group 11. The hydraulic oil directly overflows into the main return pipe and returns to the oil tank 2. When the left position of the three-position four-way electromagnetic reversing valve 116 is connected, the piston rod in the transverse support cylinder group 15 retracts. When the electromagnet DT2 is energized and DT1 is de-energized, the right position of the three-position four-way electromagnetic reversing valve 116 is connected, and the piston rod in the transverse support cylinder group 15 extends. The balance valve 118 realizes the smooth operation of the transverse support cylinder group 15 and the function of being able to stop at any position, thereby making the operation of the hydraulic system stable.

[0051] Embodiment 2:

[0052] Embodiment 2 is basically the same as Embodiment 1, and the difference is that:

[0053] A riser suspension hydraulic control system, the oil inlet end of the oil tank 2 is communicated with the oil outlet end of the second oil return filter 3.1, and the oil inlet end of the second oil return filter 3.1 is communicated with the oil outlet end of the one-way valve 5; an oil cooler 4 is arranged on the oil circuit between the first oil return filter 3 and the one-way valve 5 and on the oil circuit between the second oil return filter 3.1 and the one-way valve 5. The first oil return filter 3, the second oil return filter 3.1, and the pressure oil filter 7 are mainly used to filter the hydraulic oil in the hydraulic system; pressure sensors 9 are arranged on the oil circuits between the high-pressure one-way valve 8 and the first main control valve group 11, between the high-pressure one-way valve 8 and the second main control valve group 11.1, and between the high-pressure one-way valve 8 and the third main control valve group 11.2. The oil circuit between the high-pressure one-way valve 8 and the pressure sensor 9 is communicated with the oil inlet end of the safety valve 10. The pressure sensor 9 feeds back the pressure of the hydraulic oil on the main oil inlet road in real time. The oil outlet end of the safety valve 10 is communicated with the oil inlet end of the oil tank 2, and it mainly plays a pressure limiting and protecting role in the hydraulic system to prevent danger caused by excessive pressure in the main oil inlet road of the hydraulic system; a thermometer 1, an air filter 18, and a temperature sensor 19 are sequentially arranged on the oil tank 2.

[0054] Embodiment 3:

[0055] Embodiment 3 is basically the same as Embodiment 1, and the difference is as follows:

[0056] A riser suspension hydraulic control system, the oil outlet end of the first throttle stop valve 112 is communicated with the oil inlet port P of the three-position four-way electromagnetic directional valve 116 through a hose 115. The working oil port A of the three-position four-way electromagnetic directional valve 116 is communicated with the left free port 1182 of the balance valve 118, and the working oil port B of the three-position four-way electromagnetic directional valve 116 is communicated with the right free port 1184 of the balance valve 118. The left load port 1181 of the balance valve 118 is communicated with the oil inlet end of the transverse support cylinder group 15, and the right load port 1183 of the balance valve 118 is communicated with the oil inlet end of the transverse support cylinder group 15. The oil return port T of the three-position four-way electromagnetic directional valve 116 is communicated with the oil inlet end of the one-way valve 5 through the T2-1 port of the first main control valve group 11. The three-position four-way electromagnetic directional valve 116 realizes the control of the movement direction of the piston in the transverse support cylinder group 15; a second throttle stop valve 113 and a relief valve 114 are sequentially arranged between the oil inlet pipeline and the oil outlet pipeline of the first main control valve group 11. A main control one-way valve 117 is arranged on the balance valve 118, and a protection one-way valve 119 is arranged on the oil return oil path of the oil return port T of the three-position four-way electromagnetic directional valve 116. The balance valve 118 realizes the smooth operation of the transverse support cylinder group 15. A protection one-way valve 119 is arranged at the outlet of the oil return oil path of the three-position four-way electromagnetic directional valve 116 to prevent seawater from pouring into the oil return pipeline under pressure and eroding and damaging relatively precise valve parts such as the three-position four-way electromagnetic directional valve 116 and the balance valve 118 when the main oil return pipeline breaks.

[0057] Example 4:

[0058] Example 4 is basically the same as Example 1, except that:

[0059] A riser suspension hydraulic control system, wherein the transverse support cylinder group 15 includes a plurality of support cylinders 151. The rodless chambers of all the support cylinders 151 are communicated with the left load port 1181 of the balance valve 118, and the rod chambers of all the support cylinders 151 are communicated with the right load port 1183 of the balance valve 118. The heating valve group 13 includes a heating stop valve 132 and a throttle orifice 133. The oil outlet end of the high-pressure check valve 8 is connected to the oil inlet end of the heating stop valve 132 through the P5 port. The oil outlet end of the heating stop valve 132 is connected to the oil inlet end of the throttle orifice 133. The oil outlet end of the throttle orifice 133 is connected to the oil inlet end of the three main control valve groups 11.2 through the T5 port. A heating check valve 131 is arranged on the oil inlet end oil path of the heating stop valve 132, and a second heating check valve 134 is arranged on the oil outlet end oil path of the throttle orifice 133. The transverse support cylinder group 15 realizes the axial positioning of the rigid riser, the upper cone cylinder 16 realizes the axial locking of the rigid riser, and the lock rod cylinder group 17 realizes the axial locking of the flexible riser.

[0060] The above are only the preferred embodiments of the present invention, and the protection scope of the present invention is not limited to the above embodiments. Any equivalent modifications or changes made by those of ordinary skill in the art according to the disclosed content of the present invention shall be included in the protection scope recorded in the claims.

Claims

1. A riser suspension hydraulic control system, characterized in that : The riser suspension hydraulic control system includes an oil tank (2), a one-way valve (5), a hydraulic pump unit (6), a high-pressure one-way valve (8), a first main control valve group (11), a second main control valve group (11.1), a third main control valve group (11.2), a lateral support cylinder group (15), an upper cone cylinder (16), and a locking rod cylinder group (17); The oil outlet end of the oil tank (2) is communicated with the oil inlet end of the hydraulic pump unit (6), the oil outlet end of the hydraulic pump unit (6) is communicated with the oil inlet end of the pressure oil filter (7), the oil outlet end of the pressure oil filter (7) is communicated with the oil inlet end of the high-pressure one-way valve (8), the oil outlet end of the high-pressure one-way valve (8) is communicated with the oil inlet end P2-1 of the first main control valve group (11), a pressure reducing valve (12) is arranged between the oil path of the high-pressure one-way valve (8) and the first main control valve group (11), the oil outlet end of the high-pressure one-way valve (8) is communicated with the oil inlet end of the second main control valve group (11.1), the oil outlet end of the high-pressure one-way valve (8) is communicated with the oil inlet end of the third main control valve group (11.2), a heating valve group (13) is arranged between the oil path of the high-pressure one-way valve (8) and the third main control valve group (11.2), the oil outlet end of the first main control valve group (11) is communicated with the oil inlet end of the lateral support cylinder group (15) through an umbilical cable (14), the oil outlet end of the second main control valve group (11.1) is communicated with the oil inlet end of the upper cone cylinder (16) through an umbilical cable (14), and the oil outlet end of the third main control valve group (11.2) is communicated with the oil inlet end of the locking rod cylinder group (17) through an umbilical cable (14); The structures of the first main control valve group (11), the second main control valve group (11.1), and the third main control valve group (11.2) are the same; The first main control valve group (11) includes a flow control valve (111), a first throttle stop valve (112), a three-position four-way electromagnetic reversing valve (116), and a balance valve (118). The oil inlet end of the flow control valve (111) is communicated with the oil outlet end of the high-pressure one-way valve (8) through the P2-1 port, the oil outlet end of the flow control valve (111) is communicated with the oil inlet end of the first throttle stop valve (112), the oil outlet end of the first throttle stop valve (112) is communicated with the oil inlet end of the three-position four-way electromagnetic reversing valve (116) through a hose (115), the oil outlet end of the three-position four-way electromagnetic reversing valve (116) is communicated with the oil inlet end of the balance valve (118), and the oil outlet end of the balance valve (118) is communicated with the oil inlet end of the lateral support cylinder group (15); The oil inlet end of the oil tank (2) is communicated with the oil outlet end of a return oil filter (3), the oil inlet end of the return oil filter (3) is communicated with the oil outlet end of the one-way valve (5), the oil inlet end of the one-way valve (5) is communicated with the oil outlet end T2-1 of the first main control valve group (11), the oil inlet end of the one-way valve (5) is communicated with the oil outlet end of the second main control valve group (11.1), and the oil inlet end of the one-way valve (5) is communicated with the oil outlet end of the third main control valve group (11.2).

2. The hydraulic control system for riser suspension according to claim 1, wherein: The oil inlet end of the oil tank (2) is communicated with the oil outlet end of a second return oil filter (3.1), and the oil inlet end of the second return oil filter (3.1) is communicated with the oil outlet end of the one-way valve (5).

3. The hydraulic control system for riser suspension according to claim 2, wherein: An oil cooler (4) is provided on the oil circuit between the first oil return filter (3) and the one-way valve (5), and also on the oil circuit between the second oil return filter (3.1) and the one-way valve (5).

4. A riser suspension hydraulic control system according to claim 1, characterized in that: A thermometer (1), an air filter (18), and a temperature sensor (19) are sequentially provided on the fuel tank (2).

5. The riser suspension hydraulic control system according to any one of claims 1 to 4, characterized in that: Pressure sensors (9) are provided on the oil circuits between the high-pressure one-way valve (8) and the first main control valve group (11), between the high-pressure one-way valve (8) and the second main control valve group (11.1), and between the high-pressure one-way valve (8) and the third main control valve group (11.2). The oil circuit between the high-pressure one-way valve (8) and the pressure sensor (9) is connected to the inlet end of the safety valve (10), and the outlet end of the safety valve (10) is connected to the inlet end of the fuel tank (2).

6. The riser suspension hydraulic control system according to any one of claims 1 to 4, characterized in that: The outlet end of the first throttle stop valve (112) is connected to the inlet port P of the three-position four-way electromagnetic directional control valve (116) through a hose (115). The working port A of the three-position four-way electromagnetic directional control valve (116) is connected to the left free port (1182) of the balance valve (118), and the working port B of the three-position four-way electromagnetic directional control valve (116) is connected to the right free port (1184) of the balance valve (118). The left load port (1181) of the balance valve (118) is connected to the inlet end of the transverse support cylinder group (15), and the right load port (1183) of the balance valve (118) is connected to the inlet end of the transverse support cylinder group (15). The return port T of the three-position four-way electromagnetic directional control valve (116) is connected to the inlet end of the one-way valve (5) through the T2-1 port of the first main control valve group (11).

7. A riser suspension hydraulic control system according to claim 6, characterized in that: A second throttle stop valve (113) and a relief valve (114) are sequentially provided between the inlet pipeline and the outlet pipeline of the first main control valve group (11). A main control one-way valve (117) is provided on the balance valve (118), and a protection one-way valve (119) is provided on the return oil path of the return port T of the three-position four-way electromagnetic directional control valve (116).

8. A riser suspension hydraulic control system according to claim 7, characterized in that: The transverse support cylinder group (15) includes a plurality of support cylinders (151). The rodless chambers of all the support cylinders (151) are connected to the left load port (1181) of the balance valve (118), and the rod chambers of all the support cylinders (151) are connected to the right load port (1183) of the balance valve (118).

9. The riser suspension hydraulic control system according to any one of claims 1 to 4, characterized in that: The heating valve group (13) includes a heating stop valve (132) and a throttle orifice (133). The outlet end of the high-pressure one-way valve (8) is connected to the inlet end of the heating stop valve (132) through the P5 port. The outlet end of the heating stop valve (132) is connected to the inlet end of the throttle orifice (133), and the outlet end of the throttle orifice (133) is connected to the inlet end of the third main control valve group (11.2) through the T5 port.

10. A riser suspension hydraulic control system according to claim 9, characterized in that: A first heating one-way valve (131) is provided on the oil path at the inlet end of the heating stop valve (132), and a second heating one-way valve (134) is provided on the oil path at the outlet end of the throttle orifice (133).

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