Trestle telescopic interaction compensation control system

Abstract

According to the telescopic interactive compensation control system for the trestle bridge, when the trestle bridge needs to stretch out in the compensation process, a servo proportional reversing valve is communicated with a second oil way, hydraulic oil passes through a first one-way valve in a combination valve and then is directly connected with an A1 valve port of a single-piston-rod cylinder, a piston of the single-piston-rod cylinder is pushed to stretch out, and then the trestle bridge is driven to stretch out; in addition, active pressure relief can be achieved through a first overflow valve in the second oil way, and passive pressure relief can be achieved through a first control valve in the combination valve. When the trestle needs to retract in the compensation process, the servo proportional reversing valve communicates with a third oil way, hydraulic oil passes through a fourth one-way valve in the combination valve and then is directly connected with an A2 valve port of the single-piston-rod cylinder, a piston of the single-piston-rod cylinder is pushed to retract, in addition, active pressure relief can be achieved through a second overflow valve in the third oil way, and therefore the trestle can be effectively compensated. Passive pressure relief is achieved through a second control valve in the combination valve.

Description

Technical Field

[0001] The utility model relates to the technical field of ship trestles, in particular to a telescopic interactive compensation control system for a trestle. Background Art

[0002] With the continuous development of modern offshore operations, it is necessary to transport personnel or goods between ships, which requires the construction of a footbridge or a trestle to achieve. It is relatively simple to build on land. Since ships float on the sea surface, relative movements will occur, making it relatively difficult to build a footbridge for transporting personnel and materials between two ships on the sea. Therefore, the footbridge is generally built on one ship. If it is needed, the footbridge is set between two ships by means of lapping. In order to achieve better lapping, the relative position between the footbridge and the other ship needs to be considered. Otherwise, the footbridge and the ship will collide due to the floating of the ship. After the lapping is completed, the relative position between the two ships also needs to be considered, and the footbridge is in a passive compensation state according to the relative position of the two ships to ensure safety.

[0003] For example, in the patent document with the Chinese patent application number 201711236704.9 and the publication date of January 24, 2020, it discloses a position compensation telescopic boarding trestle luffing hydraulic system and working method, including a power system and a luffing hydraulic system; the power system includes a hydraulic oil tank, a main pump group and a high and low pressure pump group; the luffing hydraulic system includes a luffing selection valve, a luffing direction and speed control valve, a luffing accumulator control valve, a luffing accumulator switch valve, a luffing accumulator oil filling control valve, a plunger accumulator and a luffing oil cylinder.

[0004] In the above-mentioned document, the position information of the lapping point is collected by an MRU sensor and a DP system and transmitted into an industrial control computer, and calculations are carried out in the industrial control computer, and the processed signals are input to the slewing direction and speed control valve, the telescopic direction and speed control valve and the luffing direction and speed control valve. The rotation direction and speed of the slewing hydraulic motor are controlled by the slewing direction and speed control valve, the rotation direction and speed of the telescopic hydraulic motor are controlled by the telescopic direction and speed control valve, and the movement direction and speed of the luffing oil cylinder are controlled by the luffing direction and speed control valve; however, it does not disclose how to protect the oil circuit components from being affected by the excessive oil pressure in the oil circuit when the trestle is subjected to external passive forces during the active compensation process. Summary of the Utility Model

[0005] The purpose of the utility model is to provide a telescopic interactive compensation control system for a trestle, which realizes active pressure relief and passive pressure relief by setting an overflow valve and a combined valve in the hydraulic oil circuit, so as to protect the oil circuit components from being damaged by excessive oil pressure.

[0006] To achieve the above object, a telescopic interactive compensation control system for a trestle includes a first oil circuit, a servo proportional directional valve, a second oil circuit, a third oil circuit, a fourth oil circuit, a fifth oil circuit, a combination valve, a single-rod piston cylinder, an oil pump, an oil tank, and more than two overflow valves. One end of the first oil circuit is connected to the oil tank, and the other end of the first oil circuit is connected to the P1 port of the servo proportional directional valve. The P3 port of the servo proportional directional valve is connected to one end of the combination valve through the second oil circuit, and the P4 port of the servo proportional directional valve is connected to one end of the combination valve through the third oil circuit. The other end of the combination valve is connected to the single-rod piston cylinder. Overflow valves are connected between the second oil circuit and the fourth oil circuit and between the third oil circuit and the fourth oil circuit. The combination valve includes a control valve one, a control valve two, and more than two one-way valves. Both ends of the single-rod piston cylinder are respectively connected to the second oil circuit and the third oil circuit through the one-way valves. One end of the control valve one is connected to the single-rod piston cylinder, and the other end of the control valve one is connected to the third oil circuit. One end of the control valve two is connected to the single-rod piston cylinder, and the other end of the control valve two is connected to the second oil circuit. The oil tank is respectively connected to the control valve one and the control valve two through the fifth oil circuit.

[0007] With the above settings, by setting the servo proportional directional valve, the second oil circuit or the third oil circuit connected to the servo proportional directional valve can be independently controlled, and then the hydraulic oil can be controlled to drive the single-rod piston cylinder to realize the extension or retraction of the trestle, achieving the interactive compensation of the trestle in the telescopic direction after the trestle is lapped, eliminating the relative movement between the ships, and keeping the two ships relatively stationary on the sea surface. By setting the overflow valve, during the interactive compensation of the trestle through the servo proportional directional valve, if the oil pressure in the oil circuit is higher than the pressure value set by the overflow valve, the overflow valve can be made to conduct, and the hydraulic oil can flow back to the oil tank through the overflow valve and the fourth oil circuit, thereby actively reducing the oil pressure in the oil circuit and playing a backpressure role at the same time. Due to the setting of the combination valve, when the trestle is passively subjected to an external force and the oil pressure in the oil circuit connected to the combination valve is higher than the pressure value set by the control valve, the control valve can be made to conduct, and the hydraulic oil can flow back to the oil tank through the control valve and the fifth oil circuit, thereby passively reducing the oil pressure in the oil circuit and providing backpressure, better protecting the oil circuit and making the oil circuit have good reliability and a simple structure.

[0008] Further, a pressure compensation valve is provided in the first oil circuit. The oil tank is connected to one end of the pressure compensation valve through an oil pump, and the other end of the pressure compensation valve is connected to the P1 port of the servo proportional directional valve.

[0009] With the above settings, the hydraulic oil in the oil tank can be supplied into the first oil circuit through the oil pump, and the pressure of the hydraulic oil can be increased by the pressure compensation valve and flow to the servo proportional directional valve.

[0010] Further, the shuttle valve is connected to the pressure compensation valve, and both ends of the shuttle valve are respectively connected to the second oil circuit and the third oil circuit.

[0011] The above arrangement can prevent the second oil circuit and the third oil circuit from being connected at the same time.

[0012] Furthermore, the overflow valve includes overflow valve 1 and overflow valve 2, one end of overflow valve 1 is connected to the second oil circuit, one end of overflow valve 2 is connected to the third oil circuit, the other end of overflow valve 1 and the other end of overflow valve 2 are connected to the fourth oil circuit, one end of the fourth oil circuit is connected to the P2 valve port of the servo proportional reversing valve, and the other end of the fourth oil circuit is connected to the oil tank.

[0013] With the above arrangement, during the process of active compensation of the trestle through the servo proportional reversing valve, when the oil pressure in the second oil circuit is greater than the pressure value set by the relief valve 1, the relief valve 1 is turned on, so that the hydraulic oil in the second oil circuit can flow into the fourth oil circuit through the relief valve 1, and then flow back to the oil tank, actively reducing the oil pressure in the second oil circuit; when the oil pressure in the third oil circuit is greater than the pressure value set by the relief valve 2, the relief valve 2 is turned on, so that the hydraulic oil in the third oil circuit can flow into the fourth oil circuit through the relief valve 2, and then flow back to the oil tank, actively reducing the oil pressure in the third oil circuit, thereby protecting the single-piston rod cylinder and preventing damage caused by excessive oil pressure on the single-piston rod cylinder.

[0014] Furthermore, the one-way valve includes one-way valve one, one-way valve two, one-way valve three and one-way valve four, and the single-piston rod cylinder is provided with an A1 valve port and an A2 valve port. One end of the second oil circuit is connected to the P3 valve port of the servo proportional reversing valve, and one end of the one-way valve one is respectively connected to the other end of the second oil circuit and the other end of the control valve two. The A1 valve port of the single-piston rod cylinder is respectively connected to one end of the one-way valve two, one end of the control valve one and the other end of the one-way valve one.

[0015] With the above arrangement, when the piston of the single-piston rod cylinder is controlled to extend and is passively acted upon by an external force, causing the hydraulic oil pressure to be higher than the pressure value set by the control valve 1, part of the hydraulic oil can flow through the control valve 1, through the fifth oil circuit, and then back to the oil tank, thereby relieving part of the pressure.

[0016] Furthermore, one end of the third oil circuit is connected to the P4 valve port of the servo proportional reversing valve, one end of the one-way valve four is respectively connected to the other end of the third oil circuit and the other end of the control valve one, and the A2 valve port of the single-piston rod cylinder is respectively connected to one end of the one-way valve three, one end of the control valve two and the other end of the one-way valve four.

[0017] With the above arrangement, when the piston of the single-piston rod cylinder is controlled to retract and is passively acted upon by an external force, causing the hydraulic oil pressure to be higher than the pressure value set by the second control valve, part of the hydraulic oil can flow through the second control valve, through the fifth oil circuit, and then back to the oil tank, thereby relieving part of the pressure.

[0018] Further, one end of the fifth oil passage is respectively connected to the other end of the second check valve, the other end of the third check valve, the first control valve, and the second control valve, and the other end of the fifth oil passage is connected to the fuel tank.

[0019] With the above settings, the second check valve and the third check valve are respectively connected to both ends of the single-rod cylinder, which can prevent the hydraulic oil in the single-rod cylinder from directly connecting to the fifth oil passage and flowing back to the fuel tank, causing the oil pressure in the single-rod cylinder to instantly drop to zero. Instead, the hydraulic oil flowing through the first control valve and the second control valve flows back to the fuel tank through the fifth oil passage to achieve local pressure relief. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 It is a schematic structural connection diagram of the present utility model.

[0021] Figure 2 is Figure 1 the enlarged view at D in DETAILED DESCRIPTION OF THE EMBODIMENTS

[0022] The present utility model will be further described in detail below with reference to the drawings and specific embodiments.

[0023] As Figures 1 to 2 shown, a trestle telescopic interactive compensation control system includes a first oil passage 1, a shuttle valve 6, a servo-proportional directional control valve 7, a second oil passage 2, a third oil passage 3, a fourth oil passage 4, a fifth oil passage 5, a combination valve, a single-rod cylinder 8, an oil pump 9, a fuel tank 10, and more than two overflow valves.

[0024] One end of the first oil passage 1 is connected to the fuel tank 10 through the oil pump 9, and the other end of the first oil passage 1 is connected to the P1 port of the servo-proportional directional control valve 7 through a pressure compensation valve 11. In this embodiment, a pressure compensation valve 11 is provided in the first oil passage 1. The fuel tank 10 is connected to one end of the pressure compensation valve 11 through the oil pump 9, and the other end of the pressure compensation valve 11 is connected to the P1 port of the servo-proportional directional control valve 7, so that the hydraulic oil in the fuel tank 10 can be supplied into the first oil passage 1 through the oil pump 9, and the pressure of the hydraulic oil can be increased through the pressure compensation valve 11 and flow to the servo-proportional directional control valve 7. The shuttle valve 6 is connected to the pressure compensation valve 11, and both ends of the shuttle valve 11 are respectively connected to the second oil passage 2 and the third oil passage 3, and the shuttle valve 6 prevents the second oil passage 2 and the third oil passage 3 from being connected simultaneously.

[0025] The P3 port of the servo proportional reversing valve 7 is connected to one end of the combination valve through the second oil circuit 2, and the P4 port of the servo proportional reversing valve 7 is connected to one end of the combination valve through the third oil circuit 3. The other end of the combination valve is connected to the single-rod cylinder 8. In this embodiment, the combination valve includes a control valve a1, a control valve a2, and more than two one-way valves. The one-way valves include a one-way valve s1, a one-way valve s2, a one-way valve s3, and a one-way valve s4. Both ends of the single-rod cylinder 8 are respectively connected to the second oil circuit 2 and the third oil circuit 3 through one-way valves. The single-rod cylinder 8 is provided with an A1 port and an A2 port. As Figure 2 shown, one end of the second oil circuit 2 is connected to the P3 port of the servo proportional reversing valve 7. One end of the one-way valve s1 is respectively connected to the other end of the second oil circuit 2 and the control end of the control valve a2. The A1 port of the single-rod cylinder 8 is respectively connected to one end of the one-way valve s2, one end of the control valve a1, and the other end of the one-way valve s1. Thus, when the servo proportional reversing valve 7 is separately connected to the second oil circuit 2 to control the piston of the single-rod cylinder 8 to extend and is passively affected by an external force such that the oil pressure of the hydraulic oil is higher than the pressure value set by the control valve a! In this embodiment, the pressure value set by the control valve a1 is 70 bar, which can cause part of the hydraulic oil to flow back to the fuel tank 10 through the control valve a1 after flowing through the fifth oil circuit 5, thereby relieving part of the pressure. One end of the third oil circuit 3 is connected to the P4 port of the servo proportional reversing valve 7. One end of the one-way valve s4 is respectively connected to the other end of the third oil circuit 3 and the control end of the control valve a1. The A2 port of the single-rod cylinder 8 is respectively connected to one end of the one-way valve s3, one end of the control valve a2, and the other end of the one-way valve s4. Thus, when the servo proportional reversing valve 7 is separately connected to the third oil circuit 3 to control the piston of the single-rod cylinder 8 to retract and is passively affected by an external force such that the oil pressure of the hydraulic oil is higher than the pressure value set by the control valve a2. In this embodiment, the pressure value set by the control valve a2 is 70 bar, which can cause part of the hydraulic oil to flow back to the fuel tank 10 through the control valve a2 after flowing through the fifth oil circuit 5, thereby relieving part of the pressure. The fuel tank 10 is respectively connected to the control valve a1 and the control valve a2 through the fifth oil circuit 5. Specifically, one end of the fifth oil circuit 5 is respectively connected to the other end of the one-way valve s2, the other end of the one-way valve s3, the control valve a1, and the control valve a2. The other end of the fifth oil circuit 5 is connected to the fuel tank. Thus, by providing the one-way valve s2 and the one-way valve s3 to be respectively connected to both ends of the single-rod cylinder 8, it can prevent the hydraulic oil of the single-rod cylinder 8 from directly connecting to the fifth oil circuit 5 and flowing back to the fuel tank 10, causing the oil pressure of the single-rod cylinder 8 to instantly drop to zero. Instead, the hydraulic oil flowing through the control valve a1 and the control valve a2 flows back to the fuel tank 10 through the fifth oil circuit 5 to achieve local pressure relief. In this example, both the control valve a1 and the control valve a2 are overflow valves.

[0026] As Figure 1As shown, an overflow valve is connected between the second oil passage 2 and the fourth oil passage 4, and between the third oil passage 3 and the fourth oil passage 4. The overflow valve includes an overflow valve one z1 and an overflow valve two z2. One end of the overflow valve one z1 is connected to the second oil passage 2, one end of the overflow valve two z2 is connected to the third oil passage 3, the other ends of the overflow valve one z1 and the overflow valve two z2 are connected to the fourth oil passage 4. One end of the fourth oil passage 4 is connected to the P2 valve port of the servo proportional directional valve 7, and the other end of the fourth oil passage 4 is connected to the fuel tank. In this way, during the interactive compensation of the trestle through the servo proportional directional valve 7, when the oil pressure in the second oil passage 2 is greater than the pressure value set by the overflow valve one z1, in this embodiment, the pressure value set by the overflow valve one z1 is 30 bar, the overflow valve one z1 is turned on, and the hydraulic oil in the second oil passage 2 can flow into the fourth oil passage 4 through the overflow valve one z1 and then flow back to the fuel tank 10, actively reducing the oil pressure in the second oil passage 2; when the oil pressure in the third oil passage 3 is greater than the pressure value set by the overflow valve two z2, in this embodiment, the pressure value set by the overflow valve two z2 is 45 bar, the overflow valve two z2 is turned on, and the hydraulic oil in the third oil passage 3 can flow into the fourth oil passage 4 through the overflow valve two z2 and then flow back to the fuel tank 10, actively reducing the oil pressure in the third oil passage 3, thereby protecting the single-rod cylinder 8 and preventing the single-rod cylinder 8 from being damaged due to excessive oil pressure.

[0027] In this embodiment, when the servo proportional directional valve 7 is not connected to the second oil passage 2 and the third oil passage 3, the trestle is in a stationary state.

[0028] The working principle of the present invention: When the trestle needs to extend, the single piston rod will pull the single piston rod because the trestle is lapped on the ship. In this way, Figure 1 Taking the viewing direction as, when the pressure of the hydraulic oil on the right side of the single-rod cylinder is greater than the set pressure of the control valve two a2, the hydraulic oil on the right side of the single-rod cylinder will flow back to the fuel tank through the control valve two a2 and the fifth oil passage 5. At the same time, the oil pump 9 is started, the servo proportional directional valve 7 is reversed, and the oil pump 9 pumps the hydraulic oil into the first oil passage 1. The hydraulic oil entering the first oil passage 1 flows through the pressure compensation valve 11, the servo proportional directional valve 7 and the second oil passage 2. The hydraulic oil directly connects to the A1 valve port of the single-rod cylinder 8 through the check valve one s2 in the combined valve, replenishes oil to the left side of the single-rod cylinder and provides a certain oil pressure to promote the single piston rod to move to the right.

[0029] When the trestle needs to retract, the single piston rod will push the single piston rod to retract because the trestle is lapped on the ship. In this way, Figure 1Taking [[ID=]] as the viewing direction, when the pressure of the hydraulic oil on the left side of the single-rod cylinder is greater than the set pressure of the control valve a1, the hydraulic oil on the left side of the single-rod cylinder will flow back to the fuel tank through the control valve a1 and the fifth oil passage 5. At the same time, the oil pump 9 starts, and the servo-proportional reversing valve 7 reverses. The oil pump 9 pumps the hydraulic oil into the first oil passage 1. The hydraulic oil entering the first oil passage 1 flows through the pressure compensation valve 11, the servo-proportional reversing valve 7, and the third oil passage 3. The hydraulic oil directly connects to the A2 valve port of the single-rod cylinder 8 through the check valve s4 in the combined valve, replenishes oil to the right side of the single-rod cylinder and provides a certain oil pressure, prompting the single-rod cylinder to move to the left.

[0030] In this example, due to the setting of the pressure compensation valve 11, the drain end of the pressure compensation valve 11 is connected to the second oil passage 2 and the third oil passage 3 through the shuttle valve 6. In this way, when the second oil passage 2 is supplying oil and the oil pressure of the second oil passage 2 is greater than the oil pressure at the drain end of the pressure compensation valve 11, an oil pressure will be given to the drain end of the pressure compensation valve 11, and thus, the oil pressure of the second oil passage can be replenished. Similarly, if the third oil passage 3 supplies oil, based on the above principle, the oil pressure of the third oil passage will also be replenished. Due to the setting of the first relief valve and the second relief valve, when the pressure of the second oil passage is higher than the set pressure of the first relief valve, the hydraulic oil of the second oil passage will flow out from the first relief valve, so that the hydraulic oil in the second oil passage can be better controlled. When the pressure of the third oil passage is higher than the set pressure of the second relief valve, the hydraulic oil of the third oil passage will flow out from the second relief valve, so that the hydraulic oil in the third oil passage can be better controlled. Due to the setting of the combined valve, on the one hand, it is convenient for oil drainage, and on the other hand, it is to provide back pressure so that the telescoping of the trestle will not be so fast.

Claims

1. A telescopic interactive compensation control system for a trestle, comprising a first oil circuit, a servo proportional reversing valve, a second oil circuit, a third oil circuit, a fourth oil circuit, a fifth oil circuit, a combination valve, a single piston rod cylinder, an oil pump, an oil tank and more than two overflow valves, characterized in that: One end of the first oil circuit is connected to the fuel tank, and the other end of the first oil circuit is connected to the P1 valve port of the servo proportional directional valve. The P3 valve port of the servo proportional directional valve is connected to one end of the combined valve through the second oil circuit, and the P4 valve port of the servo proportional directional valve is connected to one end of the combined valve through the third oil circuit. The other end of the combined valve is connected to the single-rod piston cylinder. An overflow valve is connected between the second oil circuit and the fourth oil circuit and between the third oil circuit and the fourth oil circuit. The combined valve includes a control valve one, a control valve two, and more than two one-way valves. Both ends of the single-rod piston cylinder are respectively connected to the second oil circuit and the third oil circuit through the one-way valves. One end of the control valve one is connected to the single-rod piston cylinder, and the other end of the control valve one is connected to the third oil circuit. One end of the control valve two is connected to the single-rod piston cylinder, and the other end of the control valve two is connected to the second oil circuit. The fuel tank is connected to the control valve one and the control valve two respectively through the fifth oil circuit.

2. The telescopic interactive compensation control system for a trestle according to claim 1, wherein: A pressure compensation valve is provided in the first oil circuit. The fuel tank is connected to one end of the pressure compensation valve through an oil pump, and the other end of the pressure compensation valve is connected to the P1 valve port of the servo proportional directional valve.

3. The telescopic interactive compensation control system for a trestle according to claim 2, characterized in that: The pressure compensation valve is connected to a shuttle valve, and both ends of the shuttle valve are respectively connected to the second oil circuit and the third oil circuit.

4. The telescopic interactive compensation control system for a trestle according to claim 1, characterized in that: The overflow valve includes an overflow valve one and an overflow valve two. One end of the overflow valve one is connected to the second oil circuit, and one end of the overflow valve two is connected to the third oil circuit. The other end of the overflow valve one and the other end of the overflow valve two are connected to the fourth oil circuit. One end of the fourth oil circuit is connected to the P2 valve port of the servo proportional directional valve, and the other end of the fourth oil circuit is connected to the fuel tank.

5. The telescopic interactive compensation control system of a trestle according to claim 1, characterized in that: The one-way valves include a one-way valve one, a one-way valve two, a one-way valve three, and a one-way valve four. An A1 valve port and an A2 valve port are provided on the single-rod piston cylinder. One end of the second oil circuit is connected to the P3 valve port of the servo proportional directional valve. One end of the one-way valve one is respectively connected to the other end of the second oil circuit and the other end of the control valve two. The A1 valve port of the single-rod piston cylinder is respectively connected to one end of the one-way valve two, one end of the control valve one, and the other end of the one-way valve one.

6. The telescopic interactive compensation control system of a trestle according to claim 1, characterized in that: One end of the third oil circuit is connected to the P4 valve port of the servo proportional directional valve. One end of the one-way valve four is respectively connected to the other end of the third oil circuit and the other end of the control valve one. The A2 valve port of the single-rod piston cylinder is respectively connected to one end of the one-way valve three, one end of the control valve two, and the other end of the one-way valve four.

7. An expansion and interaction compensation control system for a trestle according to claim 1, characterized in that: One end of the fifth oil circuit is respectively connected to the other end of the one-way valve two, the other end of the one-way valve three, the control valve one, and the control valve two, and the other end of the fifth oil circuit is connected to the fuel tank.

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