CN112922912B - Wave compensation type closed rotary hydraulic control system for marine trestle - Google Patents
Wave compensation type closed rotary hydraulic control system for marine trestle Download PDFInfo
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- CN112922912B CN112922912B CN202110152563.2A CN202110152563A CN112922912B CN 112922912 B CN112922912 B CN 112922912B CN 202110152563 A CN202110152563 A CN 202110152563A CN 112922912 B CN112922912 B CN 112922912B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/26—Supply reservoir or sump assemblies
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/027—Check valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
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- Fluid Mechanics (AREA)
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- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a wave compensation type closed rotary hydraulic control system for a marine trestle, which comprises a hydraulic main circuit and an auxiliary oil source system, wherein the hydraulic circuit comprises a motor, a variable pump, a cartridge valve group, a flushing safety valve group, a reversing valve group and a motor group; the motor is respectively connected with two plug-in valve groups through a variable pump, and the two plug-in valve groups are respectively connected with the reversing valve group, the flushing safety valve and the motor group; and the variable pump is connected with the auxiliary oil source system through a proportional pressure reducing valve group. The system has the advantages that the system is provided with a set of closed pump control motor hydraulic system, can realize high-efficiency adjustment of the swing mechanism, reduces the installed power of the system, and realizes passive wave compensation after the trestle is lapped. In addition, the system also has a set of auxiliary oil source system based on the accumulator group, which not only can provide pilot control oil, but also can provide a reset oil source for the rotary hydraulic system under the condition of power failure of the power system, thereby ensuring the safety of the system.
Description
Technical Field
The invention relates to a novel wave compensation type closed rotary hydraulic control system for a marine trestle, which has the functions of rotary efficient adjustment, passive wave compensation and emergency reset.
Background
The maritime trestle is important maritime work equipment, can realize the transportation of personnel and materials under the condition of wind waves, and has wide application in offshore life platforms, offshore wind turbine maintenance ships and the like. The rotary hydraulic control system is one of the core joints of the marine trestle and needs to have the functions of rotary driving, rotary compensation and the like. The traditional design method of the rotary electro-hydraulic control system has the problems of large installed power, low efficiency, poor emergency capacity and the like, and limits the overall performance of the trestle system to a certain extent.
Disclosure of Invention
Aiming at the problems, the project designs a novel wave compensation type closed rotary hydraulic control system for a marine trestle. The system is provided with a set of closed pump control motor hydraulic system, can realize high-efficiency adjustment of the swing mechanism, and can realize passive wave compensation after the trestle is lapped. In addition, the system also has a set of auxiliary oil source system based on the accumulator group, which not only can provide pilot control oil, but also can provide a reset oil source for the rotary system under the condition of power system outage, thereby ensuring the safety of the system. The technical content of the method is as follows,
a wave compensation type closed rotary hydraulic control system for a marine trestle comprises a hydraulic main circuit and an auxiliary oil source system, wherein the hydraulic circuit comprises a motor, a variable pump, a plug-in valve bank, a flushing safety valve bank, a reversing valve bank and a motor bank; the motor is respectively connected with two plug-in valve groups through a variable pump, and the two plug-in valve groups are respectively connected with the reversing valve group, the flushing safety valve group and the motor group; and the variable pump is connected with the auxiliary oil source system through a proportional pressure reducing valve group.
Furthermore, the auxiliary oil source system comprises an auxiliary motor and an accumulator group, the auxiliary motor is connected with a one-way constant delivery pump, the one-way constant delivery pump is respectively connected with a low-pressure oil filter and a high-pressure oil filter, and the high-pressure oil filter is connected with the accumulator through a second one-way valve.
Furthermore, the auxiliary oil source system is respectively connected with a pressure reducing valve and a fourth reversing valve, the pressure reducing valve is connected with the motor set through a third reversing valve, and the fourth reversing valve is connected with the motor set through a proportional speed regulating valve and a first one-way valve in sequence.
Further, the reversing valve group comprises a first reversing valve and a second reversing valve; the proportional pressure reducing valve group comprises a first proportional pressure reducing valve, a second proportional pressure reducing valve and a third proportional pressure reducing valve; the two valve groups are respectively a first valve group and a second valve group.
Furthermore, an opening A and an opening B of the variable pump are respectively connected with an opening A of the second cartridge valve group and an opening A of the first cartridge valve group, and an opening C, an opening D and an opening E of the variable pump are respectively connected with an opening A of the first proportional pressure reducing valve, an opening A of the second proportional pressure reducing valve and an opening A of the third proportional pressure reducing valve; the port B of the second plug-in valve group is respectively connected with the port A of the flushing safety valve group, the port A of the second reversing valve, the port A of the first reversing valve and the port A of the motor group; the port B of the first plug-in valve group is respectively connected with the port B of the flushing safety valve group, the port B of the second reversing valve, the port B of the first one-way valve and the port B of the motor group; and the port A of the third reversing valve is connected with the port C of the motor group.
Furthermore, the trestle mechanism rotates forwards, the first reversing valve is positioned at the right position, the second reversing valve is positioned at the right position, the fourth reversing valve is positioned at the right position, the third reversing valve is positioned at the right position, the two cartridge valve groups are in a conducting state, the motor rotates clockwise, hydraulic oil flowing out of the second one-way valve enters the variable pump after being regulated by the proportional pressure reducing valve group, high-pressure oil flowing out of the variable pump flows into the flushing safety valve group through the second cartridge valve group, the port A of the flushing safety valve group is at high pressure, the port B of the flushing safety valve group is at low pressure, and partial hydraulic oil directly flows back to the oil tank through the port C after flowing into the flushing safety valve group through the port B of the flushing safety valve group; and hydraulic oil flowing out of the second cartridge valve group flows into the motor group, one part of the hydraulic oil flowing out of the motor group flows back to the oil tank through the flushing safety valve group, and the other part of the hydraulic oil flows into the variable displacement pump through the first cartridge valve group, so that the forward rotation of the trestle mechanism is realized.
Furthermore, the trestle mechanism rotates reversely, the first reversing valve, the second reversing valve, the fourth reversing valve and the third reversing valve are positioned on the right, the first cartridge valve group and the second cartridge valve group are in a conducting state, the motor rotates clockwise, hydraulic oil flowing out of the second one-way valve enters the variable pump after being regulated by the proportional regulating valve group, high-pressure oil flowing out of the variable pump flows into the flushing safety valve group through the first cartridge valve group, a port B of the flushing safety valve group is at high pressure, a port A of the flushing safety valve group is at low pressure, and part of the hydraulic oil directly flows back to the oil tank through a port C of the flushing safety valve group; the hydraulic oil that first cartridge valves flowed out flows into the motor group, flows back the oil tank by washing the safety valve group by motor group outflow back partly, and another part flows into the variable displacement pump by second cartridge valves, realizes the antiport of landing stage mechanism.
Further, the passive heave compensation mode: after the trestle is butted with the platform, the first reversing valve is in the right position, the second reversing valve is in the left position, the third reversing valve is in the left position, the fourth reversing valve is in the left position, the first cartridge valve and the second cartridge valve are closed and in a state, one part of hydraulic oil flowing out of the second one-way valve directly flows back to an oil tank through a pressure reducing valve, one part of hydraulic oil flows into the third reversing valve after being regulated by the pressure reducing valve, the hydraulic oil flows into the pressure motor set through the third reversing valve, and the high-pressure oil regulates the displacement of the variable motor set to be zero; hydraulic oil flowing out of the second one-way valve flows into the proportional speed regulating valve through the fourth reversing valve, the hydraulic oil flows into the first one-way valve after being regulated by the proportional speed regulating valve, a part of the hydraulic oil flows into the motor group through the one-way valve, a part of the hydraulic oil flows into the port A of the flushing safety valve group through the second reversing valve, and the other part of the hydraulic oil directly enters the port B of the flushing safety valve group, so that the ports A and B of the flushing safety valve group are at the same pressure, and no hydraulic oil flows into the flushing safety valve group at this time; and hydraulic oil flowing out of the second reversing valve enters the motor set to supplement oil for the motor set.
Furthermore, the power system of the trestle mechanism is powered off accidentally (the weak current system adopts a standby battery for power supply), the first reversing valve is positioned at the left position, the second reversing valve is positioned at the right position, the third reversing valve is positioned at the right position, the fourth reversing valve is positioned at the left position, the first cartridge valve and the second cartridge valve are positioned in a closed state, hydraulic oil in the energy accumulator group flows into the motor group through the fourth reversing valve, the proportional speed regulating valve and the first one-way valve, flows into the first reversing valve from the motor group, flows back to the oil tank from the first reversing valve, and the reset motion of the trestle system under the condition of accidental power off is realized under the action of the hydraulic oil in the energy accumulator group.
Advantageous effects
1) The system is provided with a set of closed pump control motor hydraulic system, can realize high-efficiency adjustment of the swing mechanism, increases the system efficiency, reduces the installed power of the system, and realizes passive wave compensation after the trestle is lapped.
2) The system also has an auxiliary oil source system based on an accumulator group, which not only can provide pilot control oil, but also can provide a reset oil source for the rotary system under the condition of power failure of the power system, thereby ensuring the safety of the system.
Drawings
FIG. 1 is a schematic diagram of the present application;
FIG. 2 is an enlarged view of portion A of FIG. 1;
FIG. 3 is an enlarged view of portion B of FIG. 1;
FIG. 4 is an enlarged view of portion C of FIG. 1;
FIG. 5 is an enlarged view of portion D of FIG. 1;
wherein 1-a first reversing valve, 2-a first variable motor, 3-a second variable motor, 4-a third variable motor, 5-a second reversing valve, 6-a third reversing valve, 7-a pressure reducing valve, 8-a fourth reversing valve, 9-a proportional speed regulating valve, 10-a first check valve, 11-a flushing safety valve bank, 12-a first energy accumulator, 13-a second energy accumulator, 14-a third energy accumulator, 15-a fourth energy accumulator, 16-a second check valve, 17-an overflow valve, 18-a high-pressure oil filter, 19-a one-way fixed displacement pump, 20-a low-pressure oil filter, 21-an auxiliary motor, 22-a first cartridge valve bank, 23-a second cartridge valve bank, 24-a first proportion valve, 25-a second proportional pressure reducing valve and 26-a third proportional pressure reducing valve, 27-variable pump, 28-motor, 29-oil tank.
Detailed Description
The following detailed description is exemplary and is intended to provide further explanation of the invention as claimed. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments according to the present application.
The invention comprises a reversing valve set (a first reversing valve 1 adopts a two-position two-way electromagnetic reversing valve, a second reversing valve 5 adopts a two-position two-way electromagnetic reversing valve, a third reversing valve 6 adopts a two-position three-way electromagnetic reversing valve and a fourth reversing valve 8 adopts a two-position two-way electromagnetic reversing valve), a motor set comprises a variable motor I2, a variable motor II 3 and a variable motor 3, a pressure reducing valve 7 adopts a manual pressure reducing valve, a proportional speed regulating valve 9, a first one-way valve 10, a flushing safety valve set 11, an energy accumulator set (an energy accumulator I12, an energy accumulator II 13, an energy accumulator III 14, an energy accumulator IV 15), a second one-way valve 16, an overflow valve 17, a high-pressure oil filter 18, a one-way constant delivery pump 19, a low-pressure oil filter 20 and an auxiliary motor 21 (a three-phase asynchronous motor), the two cartridge valve sets are respectively a first cartridge valve set 22, a second cartridge valve set 23 and a proportional pressure reducing valve set (a first cartridge valve set 24, a first cartridge valve set, A second proportional pressure reducing valve 25, a third proportional pressure reducing valve 26), a variable pump 27, a motor 28 (three-phase asynchronous motor), and an oil tank 29.
A hydraulic main loop of the system: the port A of the variable pump 27 is connected with the port A of the second cartridge valve group 23 (two-way cartridge valve group); the port B of the variable pump 27 is connected with the port A of the first cartridge valve group 22 (two-way cartridge valve group); the port C of the variable pump 27 is connected with the port A of the proportional pressure reducing valve 24; the D port of the variable pump 27 is connected with the A port of the second proportional pressure reducing valve 25; the port E of the variable pump 27 is connected with the port A of the third proportional pressure reducing valve 26; the port C of the first proportional pressure reducing valve 24 is connected to the tank 29; the port C of the second proportional pressure reducing valve 25 is connected with an oil tank 29; the port C of the third proportional pressure reducing valve 26 is connected to the oil tank 29; the port C of the second cartridge valve group 23 is connected with an oil tank 29; the port C of the first cartridge valve group 22 is connected with an oil tank 29; the port B of the second plug-in valve group 23 is respectively connected with the port A of the flushing safety valve group 11, the port A of the second reversing valve 5, the port A of the first reversing valve 1, the port A of the first variable motor 2, the port A of the second variable motor 3 and the port A of the third variable motor 4; the port B of the first plug-in valve group 22 is respectively connected with the port 11B of the flushing safety valve group 11, the port B of the second reversing valve 5, the port B of the first check valve 10, the port B of the first variable motor 2, the port B of the second variable motor 3 and the port B of the third variable motor 4; the port B of the first reversing valve 1 is connected with an oil tank 29; the port C of the flushing safety valve group 11 is connected with an oil tank 29; port a of the low-pressure oil filter 20 is connected to the oil tank 29; the port B of the low-pressure oil filter 20 is connected with the port A of the one-way fixed displacement pump 19; the port B of the one-way constant delivery pump 19 is connected with the port A of the high-pressure oil filter 18; the port B of the high-pressure oil filter is respectively connected with the port A of the second one-way valve 16 and the port A of the overflow valve 17; the port B of the overflow valve 17 is connected with an oil tank 29; the port B of the second check valve 16 is respectively connected with the port B of the first proportional pressure reducing valve 24, the port B of the second proportional pressure reducing valve 25, the port B of the third proportional pressure reducing valve 26, the port A of the first accumulator 12, the port A of the second accumulator 13, the port A of the third accumulator 14, the port A of the fourth accumulator 15, the port B of the manual pressure reducing valve 7 and the port A of the fourth reversing valve 8; the port B of the fourth reversing valve 8 is connected with the port A of the proportional speed regulating valve 9; the port B of the proportional speed control valve 9 is connected with the port A of the first one-way valve 10; the port C of the manual pressure reducing valve 7 is connected with an oil tank 29; the port A of the manual pressure reducing valve 7 is connected with the port B of the third reversing valve 6; the port C of the third reversing valve 6 is connected with an oil tank 29; the port A of the third reversing valve 6 is respectively connected with the port C of the first variable motor 2, the port C of the second variable motor 3 and the port C of the third variable motor 4.
When the first reversing valve 1, the second reversing valve 5 and the fourth reversing valve 8 are in the left position, the A port is communicated with the B port; when the valve is at the right position, the port A and the port B are disconnected.
When the third reversing valve 6 is in the left position, the port A is communicated with the port B, and the port A is disconnected with the port C; when the valve is at the right position, the port A is disconnected with the port B, and the port A is communicated with the port C.
The first valve cartridge assembly 22 and the second valve cartridge assembly 23 are in a conducting state, and the port A and the port B are communicated; the first and second valve cartridge blocks 22 and 23 are in a closed state, and ports a and B thereof are disconnected.
When the flushing safety valve group 11 is in the first state, the port a of the flushing safety valve group 11 is at a high pressure, the port B of the flushing safety valve group 11 is at a low pressure, and at the moment, part of hydraulic oil directly flows back to the oil tank 29 from the port C after flowing into the flushing safety valve group 11 through the port B.
When the flushing safety valve group 11 is in the second state, the port a of the flushing safety valve group 11 is at a low pressure, the port B of the flushing safety valve group 11 is at a high pressure, and at the moment, part of hydraulic oil directly flows back to the oil tank 29 from the port C after flowing into the flushing safety valve group 11 through the port a.
When the flushing safety valve set 11 is in the third state, the port a of the flushing safety valve set 11 and the port B of the flushing safety valve set 11 are at the same pressure, and no hydraulic oil flows into the flushing safety valve set 11 at this time.
Auxiliary oil source system: when the auxiliary motor 21 rotates, the hydraulic oil in the oil tank 29 flows into the low-pressure oil filter 20 through the port A of the low-pressure oil filter 20, the hydraulic oil flows out from the port B of the low-pressure oil filter 20, the hydraulic oil flowing out from the port B flows into the one-way constant delivery pump 19 through the port A of the one-way constant delivery pump 19, the hydraulic oil flowing out from the port B flows out from the port B of the one-way constant delivery pump 19, the hydraulic oil flowing out from the port B flows into the high-pressure oil filter 18 through the port A of the high-pressure oil filter 18, the hydraulic oil flowing out from the port B of the high-pressure oil filter 18 flows out from the port B of the one-way valve 16 through the port A of the overflow valve 17, the hydraulic oil flows into the overflow valve 17 through the port A of the overflow valve 17, and the hydraulic oil directly flows back to the oil tank 29 through the port B of the overflow valve 17 after passing through the overflow valve 17, the hydraulic oil flowing out of the port B of the second check valve 16 is used as an auxiliary oil source of the whole hydraulic system, meanwhile, the hydraulic oil flowing out of the port B of the check valve 16 is used for charging the first energy accumulator 12 through the port A of the first energy accumulator 12, charging the second energy accumulator 13 through the port A of the second energy accumulator 13, charging the third energy accumulator 14 through the port A of the third energy accumulator 14, and charging the fourth energy accumulator 15 through the port A of the fourth energy accumulator 15.
The trestle mechanism rotates positively: the first reversing valve 1 is in a right position, the second reversing valve 5 is in a right position, the fourth reversing valve 8 is in a right position, the third reversing valve 6 is in a right position, the first valve cartridge 22 is in a conducting state, the second valve cartridge 23 is in a conducting state, the motor 28 rotates clockwise, hydraulic oil flowing out of the port B of the second one-way valve 16 flows into the first proportional pressure reducing valve 24 through the port B of the proportional pressure reducing valve 24, a part of the hydraulic oil flowing into the first proportional pressure reducing valve 24 directly flows back to the oil tank 29 through the port C of the first proportional pressure reducing valve 24, a part of the hydraulic oil flows out of the port A of the first proportional pressure reducing valve 24 after being regulated by the first proportional pressure reducing valve 24, and the hydraulic oil flowing out of the port A of the first proportional pressure reducing valve 24 flows into the variable pump 27 through the port C of the variable pump 27; the hydraulic oil flowing out of the port B of the second check valve 16 flows into the second proportional pressure reducing valve 25 through the port B of the second proportional pressure reducing valve 25, a part of the hydraulic oil flowing into the second proportional pressure reducing valve 25 directly flows back to the oil tank 29 through the port C of the second proportional pressure reducing valve 25, a part of the hydraulic oil is regulated into high-pressure oil through the second proportional pressure reducing valve 25 and then flows out of the port A of the second proportional pressure reducing valve 25, and the hydraulic oil flowing out of the port A of the second proportional pressure reducing valve 25 flows into the variable pump 27 through the port D of the variable pump 27; the hydraulic oil flowing out of the port B of the second check valve 16 flows into the third proportional pressure reducing valve 26 through the port B of the third proportional pressure reducing valve 26, a part of the hydraulic oil flowing into the third proportional pressure reducing valve 26 directly flows back to the oil tank 29 through the port C of the third proportional pressure reducing valve 26, a part of the hydraulic oil is adjusted to be zero pressure through the third proportional pressure reducing valve 26 and then flows out through the port A thereof, the hydraulic oil flowing out of the port A of the third proportional pressure reducing valve 26 flows into the variable pump 27 through the port E of the variable pump 27, the hydraulic oil flowing into the variable pump 27 from the port C supplements the hydraulic oil of a certain pressure for the whole hydraulic system at the moment, the displacement of the variable pump 27 is adjusted by adjusting the pressure difference between the hydraulic oil flowing into the port D of the variable pump 27 and the port E, the hydraulic oil flowing out of the port A of the variable pump 27 flows into the second valve plug-in valve block 23 through the port A of the second valve block 23, and the hydraulic oil flows out through the port B of the second valve block 23, the hydraulic oil flowing out from the port B of the second valve assembly 23 flows into the flushing valve assembly 11 through the port A of the flushing valve assembly 11 to enable the flushing valve assembly 11 to be in the first state, the hydraulic oil flowing out from the port B of the second valve assembly 23 flows into the variable motor I2 through the port A of the variable motor I2, flows into the variable motor II 3 through the port A of the variable motor II 3, flows into the variable motor III 4 through the port A of the variable motor III 4, flows out from the port B of the variable motor I2, flows out from the port B of the variable motor II 3, flows out from the port B of the variable motor III 4, flows into the flushing valve assembly 11 through the port B of the flushing valve assembly 11, flows into the first valve assembly 22 through the port B of the first valve assembly 22, flows into the hydraulic oil tank 29 directly through the port C of the flushing valve assembly 11, the hydraulic oil flowing into the first valve cartridge 22 from the port B flows out through the port a, and the hydraulic oil flowing out of the port a of the first valve cartridge 22 flows into the variable pump 27 through the port B of the variable pump 27, so that the forward rotation of the trestle mechanism is realized.
The trestle mechanism rotates reversely: the first reversing valve 1 is in a right position, the second reversing valve 5 is in a right position, the fourth reversing valve 8 is in a right position, the third reversing valve 6 is in a right position, the first cartridge valve group 22 is in a conducting state, the second cartridge valve group 23 is in a conducting state, the motor 28 rotates clockwise, hydraulic oil flowing out of the port B of the second one-way valve 16 flows into the first proportional pressure reducing valve 24 through the port B of the first proportional pressure reducing valve 24, a part of the hydraulic oil flowing into the first proportional pressure reducing valve 24 directly flows back to the oil tank 29 through the port C of the first proportional pressure reducing valve 24, a part of the hydraulic oil flows out of the port A of the first proportional pressure reducing valve 24 after being regulated by the first proportional pressure reducing valve 24, and the hydraulic oil flowing out of the port A of the first proportional pressure reducing valve 24 flows into the variable pump 27 through the port C of the variable pump 27; the hydraulic oil flowing out of the port B of the second check valve 16 flows into the second proportional pressure reducing valve 25 through the port B of the second proportional pressure reducing valve 25, a part of the hydraulic oil flowing into the second proportional pressure reducing valve 25 directly flows back to the oil tank 29 through the port C of the second proportional pressure reducing valve 25, a part of the hydraulic oil is adjusted to be zero pressure by the second proportional pressure reducing valve 25 and then flows out of the port A of the second proportional pressure reducing valve 25, and the hydraulic oil flowing out of the port A of the second proportional pressure reducing valve 25 flows into the variable pump 27 through the port D of the variable pump 27; the hydraulic oil flowing out of the port B of the second check valve 16 flows into the third proportional pressure reducing valve 26 through the port B of the third proportional pressure reducing valve 26, a part of the hydraulic oil flowing into the third proportional pressure reducing valve 26 directly flows back to the oil tank 29 through the port C of the third proportional pressure reducing valve 26, a part of the hydraulic oil is adjusted to be high-pressure oil through the third proportional pressure reducing valve 26 and then flows out from the port A thereof, the hydraulic oil flowing out of the port A of the third proportional pressure reducing valve 26 flows into the variable pump 27 through the port E of the variable pump 27, the hydraulic oil flowing into the variable pump 27 from the port C of the variable pump 27 supplements the hydraulic oil of a certain pressure for the whole hydraulic system at the moment, the displacement of the variable pump 27 is adjusted by adjusting the pressure difference of the hydraulic oil of the port D and the port E of the variable pump 27, the hydraulic oil flowing out of the port B of the variable pump 27 flows into the first cartridge valve group 22 through the port A of the first valve group 22, and the hydraulic oil flows out from the port B thereof after passing through the first valve group 22, the hydraulic oil flowing out of the port B flows into the flushing safety valve group 11 through the port B of the flushing safety valve group 11 to enable the flushing safety valve group 11 to be in a state II, the hydraulic oil flowing out of the port B flows into the variable motor I2 through the port B of the variable motor I2, flows into the variable motor II 3 through the port B of the variable motor II 3, flows into the variable motor III 4 through the port B of the variable motor III 4, flows out of the hydraulic oil through the port A of the variable motor I2, flows out of the hydraulic oil through the port A of the variable motor II 3, flows out of the hydraulic oil through the port A of the variable motor III 4, flows into the flushing safety valve group 11 through the port A of the flushing safety valve group 11, flows into the second plug-in valve group 23 through the port B of the second plug-in valve group 23, directly flows back to the oil tank 29 through the port C of the hydraulic oil flowing into the port B of the second plug-in valve group 23, and flows out of the hydraulic oil flowing into the port A of the second plug-in valve group 23 through the port A of the port B of the second plug-in valve group 23, the hydraulic oil flowing out of the port A flows into the variable pump 27 through the port A of the variable pump 27, and the reverse rotation of the trestle mechanism is realized.
Passive heave compensation mode: after the trestle is butted with a platform, the first reversing valve 1 is at the right position, the second reversing valve 5 is at the left position, the third reversing valve 6 is at the left position, the fourth reversing valve 8 is at the left position, the first cartridge valve 22 is at the closed state, the second cartridge valve 23 is at the closed state, hydraulic oil flowing out of the port B of the second one-way valve 16 flows into the manual pressure reducing valve 7 through the port B of the manual pressure reducing valve 7, a part of the hydraulic oil flowing into the manual pressure reducing valve 7 directly flows back to the oil tank 29 through the port C of the manual pressure reducing valve 7, a part of the hydraulic oil flows out through the port A of the manual pressure reducing valve 7 after being regulated by the manual pressure reducing valve 7, the hydraulic oil flowing out of the port A of the manual pressure reducing valve 7 flows into the third reversing valve 6 through the port B of the third reversing valve 6, the hydraulic oil flows out of the port A of the third reversing valve 6 respectively flows into the hydraulic variable motor one 2 through the port C of the hydraulic variable motor one 2, the hydraulic oil flows into the variable motor II 3 through the port C of the variable motor II 3, flows into the variable motor III 4 through the port C of the variable motor III 4, flows into the high-pressure oil of the variable motor I2 from the port C of the variable motor I2 to adjust the displacement of the variable motor I2 to 0, flows into the high-pressure oil of the variable motor II 3 from the port C of the variable motor II 3 to adjust the displacement of the variable motor II 3 to 0, flows into the high-pressure oil of the variable motor III 4 from the port C of the variable motor III 4 to adjust the displacement of the variable motor III 4 to 0, flows out from the port B of the second one-way valve 16 through the port A of the fourth one-way valve 8 to flow into the third one-way valve 8, flows out from the port B of the fourth one-way valve 8 through the port B thereof, flows out from the port B of the fourth one-way valve 8 through the port A of the proportional speed-adjusting valve 9, flows out from the port B of the proportional speed-adjusting valve 9 through the port B of the proportional speed valve 9 after being adjusted, and flows out from the port B of the first one-way valve 10 The hydraulic oil flows out from the port B of the first check valve 10 after passing through the first check valve 10, the hydraulic oil flowing out from the port B of the first check valve 10 flows into the variable motor I2 through the port B of the variable motor I2, flows into the variable motor II 3 through the port B of the variable motor II 3, flows into the variable motor III 4 through the port B of the variable motor III 4, the hydraulic oil flowing out from the port B of the first check valve 10 flows into the second reversing valve 5 through the port B of the second reversing valve 5, the hydraulic oil flows out from the port A of the second reversing valve 5 after passing through the second reversing valve 5, the flushing safety valve group 11 is in the state III, the hydraulic oil flowing out from the port A of the second reversing valve 5 flows into the variable motor I2 through the port A of the variable motor I2, flows into the variable motor II 3 through the port A of the variable motor II 3, flows into the variable motor III 4 through the port A of the variable motor III 4, and the hydraulic oil flowing into the ports A of the variable motor I2 and the port B of the variable motor I2 is supplemented oil for the variable motor I2, the hydraulic oil flowing into the second variable motor 3 from the port A and the port B of the second variable motor 3 is used as oil supplement for the second variable motor 3, and the hydraulic oil flowing into the third variable motor 4 from the port A and the port B of the third variable motor 4 is used as oil supplement for the third variable motor 4, so that passive wave compensation motion of the trestle along with wave fluctuation is realized.
Unexpected outage of landing stage mechanism driving system, landing stage system's reset function: when the power system of the trestle is powered off accidentally and the variable displacement pump 27 cannot continuously provide hydraulic oil to reset the trestle, the reversing valve group of the system is powered by the standby battery and does not lose efficacy, the first reversing valve 1 is at the left position, the second reversing valve 5 is at the right position, the third reversing valve 6 is at the right position, the fourth reversing valve 8 is at the left position, the first cartridge valve 22 is at the closed state, the second cartridge valve 23 is at the closed state, the hydraulic oil in the energy accumulator I12 flows out through the port A thereof, the hydraulic oil in the energy accumulator II 13 flows out through the port A thereof, the hydraulic oil in the energy accumulator III 14 flows out through the port A thereof, the hydraulic oil in the energy accumulator IV 15 flows out through the port A thereof, the hydraulic oil flowing out from the port A of the energy accumulator group flows into the fourth reversing valve 8 through the port A of the fourth reversing valve 8, the hydraulic oil flowing into the fourth reversing valve 8 flows out through the port B thereof, the hydraulic oil flowing out from the port B of the fourth reversing valve 8 flows into the proportional speed regulating valve 9 through the port A of the proportional speed regulating valve 9, the hydraulic oil flows out from the port B of the proportional speed regulating valve 9 after being regulated by the proportional speed regulating valve 9, the hydraulic oil flowing out from the port B of the proportional speed regulating valve 9 flows into the first one-way valve 10 through the port A of the first one-way valve 10, the hydraulic oil flows out from the port B of the first one-way valve 10 through the port B of the variable motor three 4, flows into the variable motor two 3 through the port B of the variable motor two 3, flows into the variable motor one 2 through the port B of the variable motor one 2, flows out from the port A of the variable motor one 2 after passing through the variable motor two 3, flows out from the port A of the variable motor three 4, flows out from the port A of the variable motor group, flows into the first reversing valve 1 through the port A of the first reversing valve 1 together with the hydraulic oil flowing out of the stack bridge system, directly flows back to the oil tank 29 through the port B of the first reversing valve 1, and realizes the reset unexpected outage of the stack bridge system under the action of the hydraulic oil in the energy storage group And (6) moving.
The above description is only a preferred embodiment of the present application and is not intended to limit the present application, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, improvement and the like made within the spirit and principle of the present application shall be included in the protection scope of the present application.
Claims (5)
1. A wave compensation type closed rotary hydraulic control system for a marine trestle is characterized by comprising a hydraulic main loop and an auxiliary oil source system, wherein the hydraulic main loop comprises a motor, a variable pump, a cartridge valve bank, a flushing safety valve bank, a reversing valve bank, a motor bank and a proportional pressure reducing valve bank;
the variable pump comprises a working oil port A, a working oil port B, a pilot oil port D, a pilot oil port E and an oil supplementing port C;
the reversing valve group comprises a first reversing valve, a second reversing valve, a third reversing valve and a fourth reversing valve, the proportional pressure reducing valve group comprises a first proportional pressure reducing valve, a second proportional pressure reducing valve and a third proportional pressure reducing valve, and the two plug-in valve groups are respectively a first plug-in valve group and a second plug-in valve group;
the port A of the variable pump is connected with the port A of the second plug-in valve group; a port B of the variable pump is connected with a port A of the first cartridge valve group, a port C of the variable pump is connected with a port A of the first proportional pressure reducing valve, a port D of the variable pump is connected with a port A of the second proportional pressure reducing valve, and a port E of the variable pump is connected with a port A of the third proportional pressure reducing valve; the port B of the second plug-in valve group is respectively connected with the port A of the flushing safety valve group, the port A of the second reversing valve, the port A of the first reversing valve and the port A of the motor group; the port B of the first plug-in valve group is respectively connected with the port B of the flushing safety valve group, the port B of the second reversing valve and the port B of the motor group; the port B of the first proportional pressure reducing valve, the port B of the second proportional pressure reducing valve and the port B of the third proportional pressure reducing valve are connected with an auxiliary oil source system; the port C of the first proportional pressure reducing valve, the port C of the second proportional pressure reducing valve, the port C of the first cartridge valve group, the port C of the second cartridge valve group, the port C of the third proportional pressure reducing valve, the port B of the first reversing valve and the port C of the flushing safety valve group are connected with an oil tank;
the auxiliary oil source system comprises an auxiliary motor and an accumulator group, the auxiliary motor is connected with a one-way constant delivery pump, the one-way constant delivery pump is respectively connected with a low-pressure oil filter and a high-pressure oil filter, and the high-pressure oil filter is connected with the accumulator group through a second one-way valve;
the port A of the low-pressure oil filter is connected with the oil tank, and the port B of the low-pressure oil filter is connected with the port A of the one-way constant delivery pump; the port B of the unidirectional constant delivery pump is connected with the port A of the high-pressure oil filter; the port B of the high-pressure oil filter is respectively connected with the port A of the second one-way valve and the port A of the overflow valve; the port B of the overflow valve is connected with an oil tank; the port B of the second one-way valve is respectively connected with the port B of the first proportional pressure reducing valve, the port B of the second proportional pressure reducing valve, the port B of the third proportional pressure reducing valve, the port A of the accumulator group, the port B of the pressure reducing valve and the port A of the fourth reversing valve; the port B of the fourth reversing valve is connected with the port A of the proportional speed regulating valve; the port B of the proportional speed regulating valve is connected with the port A of the first one-way valve; the port C of the pressure reducing valve is connected with the oil tank; the port A of the pressure reducing valve is connected with the port B of the third reversing valve; the port C of the third reversing valve is connected with the oil tank; and the port A of the third reversing valve is respectively connected with the port C of the motor group.
2. The wave compensation type closed rotary hydraulic control system for the marine trestle according to claim 1, wherein the trestle mechanism rotates in a forward direction, the first reversing valve is in a right position, the second reversing valve is in a right position, the fourth reversing valve is in a right position, the third reversing valve is in a right position, the first cartridge valve group is in a conducting state, the second cartridge valve group is in a conducting state, the auxiliary motor rotates clockwise, hydraulic oil flowing out of a port B of the second one-way valve flows into the first proportional pressure reducing valve, a part of the hydraulic oil flowing into the first proportional pressure reducing valve directly flows back to an oil tank through a port C of the first proportional pressure reducing valve, a part of the hydraulic oil flows out of a port A of the first proportional pressure reducing valve after being regulated by the first proportional pressure reducing valve, and the hydraulic oil flowing out of the port A of the first proportional pressure reducing valve flows into the variable pump through a port C of the variable pump; the hydraulic oil flowing out of the port B of the second one-way valve flows into the second proportional pressure reducing valve through the port B of the second proportional pressure reducing valve, one part of the hydraulic oil flowing into the second proportional pressure reducing valve directly flows back to the oil tank through the port C of the second proportional pressure reducing valve, one part of the hydraulic oil flows out of the port A of the second proportional pressure reducing valve after being regulated by the second proportional pressure reducing valve, and the hydraulic oil flowing out of the port A of the second proportional pressure reducing valve flows into the variable pump through the port D of the variable pump; the hydraulic oil flowing out of the port B of the second check valve flows into the third proportional pressure reducing valve through the port B of the third proportional pressure reducing valve, part of the hydraulic oil flowing into the third proportional pressure reducing valve directly flows back to the oil tank through the port C of the third proportional pressure reducing valve, part of the hydraulic oil is adjusted to be zero pressure through the third proportional pressure reducing valve and then flows out of the port A of the third proportional pressure reducing valve, the hydraulic oil flowing out of the port A of the third proportional pressure reducing valve flows into the variable pump through the port E of the variable pump, the hydraulic oil flowing into the variable pump from the port C of the variable pump supplements the hydraulic oil with certain pressure for the whole hydraulic system at the moment, the displacement of the variable pump is adjusted by adjusting the pressure difference of the hydraulic oil flowing into the port D and the port E of the variable pump, the hydraulic oil flowing out of the port A of the variable pump flows into the second cartridge valve group through the port A of the second valve group, the hydraulic oil flows out of the port B of the second cartridge valve group, and the hydraulic oil flowing out of the port B of the second cartridge valve group flows into the flushing safety valve group through the port A of the flushing valve group, the flushing safety valve group is in a first state, at the moment, part of hydraulic oil flows into the flushing safety valve group through a port B and then directly flows back to an oil tank through a port C, the hydraulic oil flowing out of the port B of the second cartridge valve group flows into a port A of the variable displacement motor group and flows out of a port B of the variable displacement motor group, the hydraulic oil flowing out of the port B of the motor group flows into the flushing safety valve group through the port B of the flushing safety valve group and flows into the first cartridge valve group through the port B of the first cartridge valve group, the hydraulic oil flowing into the flushing safety valve group directly flows back to the oil tank through the port C of the flushing safety valve group, the hydraulic oil flowing into the first cartridge valve group through the port B of the variable displacement pump flows into the variable displacement pump through the port A of the variable displacement pump, and forward rotation of the trestle mechanism is achieved.
3. The wave compensation type closed rotary hydraulic control system for the marine trestle according to claim 1, wherein the trestle mechanism rotates reversely, the first reversing valve is in a right position, the second reversing valve is in a right position, the fourth reversing valve is in a right position, the third reversing valve is in a right position, the first cartridge valve group is in a conducting state, the second cartridge valve group is in a conducting state, the auxiliary motor rotates clockwise, hydraulic oil flowing out of a port B of the second check valve flows into the first proportional pressure reducing valve through a port B of the first proportional pressure reducing valve, a part of the hydraulic oil flowing into the first proportional pressure reducing valve directly flows back to an oil tank through a port C of the first proportional pressure reducing valve, a part of the hydraulic oil flows out of a port A of the first proportional pressure reducing valve after being regulated by the first proportional pressure reducing valve, and the hydraulic oil flowing out of the port A of the first proportional pressure reducing valve flows into the variable pump through a port C of the variable pump; the hydraulic oil flowing out of the port B of the second one-way valve flows into the second proportional pressure reducing valve through the port B of the second proportional pressure reducing valve, one part of the hydraulic oil flowing into the second proportional pressure reducing valve directly flows back to the oil tank through the port C of the second proportional pressure reducing valve, one part of the hydraulic oil is adjusted to be zero pressure by the second proportional pressure reducing valve and then flows out of the port A of the second proportional pressure reducing valve, and the hydraulic oil flowing out of the port A of the second proportional pressure reducing valve flows into the variable pump through the port D of the variable pump; the hydraulic oil flowing out of the port B of the second one-way valve flows into a third proportional pressure reducing valve through the port B of the third proportional pressure reducing valve, part of the hydraulic oil flowing into the third proportional pressure reducing valve directly flows back to an oil tank through the port C of the third proportional pressure reducing valve, part of the hydraulic oil flows out of the port A of the third proportional pressure reducing valve after being regulated by the third proportional pressure reducing valve, the hydraulic oil flowing out of the port A of the third proportional pressure reducing valve flows into a variable pump through the port E of the variable pump, the hydraulic oil flowing into the variable pump from the port C of the variable pump supplements the hydraulic oil with certain pressure for the whole hydraulic system at the moment, the discharge capacity of the variable pump is adjusted by adjusting the pressure difference of the hydraulic oil of the port D and the port E of the variable pump, the hydraulic oil flowing out of the port B of the variable pump flows into a first cartridge valve group through the port A of the first cartridge valve group, the hydraulic oil flows out of the port B of the first cartridge valve group, and the hydraulic oil flowing out of the port B of the flushing safety valve group, and the flushing safety valve group is in a second state, part of hydraulic oil flows into the flushing safety valve group through the port A and then directly flows back to the oil tank through the port C, the hydraulic oil flowing out of the port B flows into the motor group through the port B of the motor group and flows out of the port A, the hydraulic oil flowing out of the port A of the motor group flows into the flushing valve through the port A of the flushing safety valve group and flows into the second cartridge valve group through the port B of the second cartridge valve group, the hydraulic oil flowing into the flushing safety valve group directly flows back to the oil tank through the port C of the motor group, the hydraulic oil flowing into the second cartridge valve group through the port B of the second cartridge valve group flows out through the port A of the second cartridge valve group, and the hydraulic oil flowing out of the port A flows into the variable pump through the port A of the variable pump, so that the reverse rotation of the trestle mechanism is realized.
4. The wave compensation type closed-type rotary hydraulic control system for the marine trestle according to claim 1, characterized in that in a passive wave compensation mode: when the trestle is butted with the platform, the first reversing valve is in the right position, the second reversing valve is in the left position, the third reversing valve is in the left position, the fourth reversing valve is in the left position, the first cartridge valve is in a closed state, the second cartridge valve is in a closed state, hydraulic oil flowing out of the port B of the second one-way valve flows into the pressure reducing valve through the port B of the pressure reducing valve, a part of hydraulic oil flowing into the pressure reducing valve directly flows back to the oil tank through the port C of the pressure reducing valve, a part of hydraulic oil flows out of the port A of the pressure reducing valve through the port A of the pressure reducing valve, the hydraulic oil flowing out of the port A of the pressure reducing valve flows into the third reversing valve through the port B of the third reversing valve, the hydraulic oil flows out of the port A of the third reversing valve through the port A of the third reversing valve, the hydraulic oil flowing out of the port A of the third reversing valve flows into the motor group through the port C of the motor group, the displacement of the motor group is adjusted to be 0, and the hydraulic oil flowing out of the port B of the second one-way through the port A of the fourth reversing valve, hydraulic oil flows into the proportional speed regulating valve from a port B of the proportional speed regulating valve after passing through the fourth reversing valve, the hydraulic oil flows out of the port B of the proportional speed regulating valve after being regulated by the proportional speed regulating valve, the hydraulic oil flowing out of the port B of the proportional speed regulating valve flows into the first one-way valve through the port A of the first one-way valve, the hydraulic oil flowing out of the port B of the first one-way valve flows into the motor group through the port B of the motor group, the hydraulic oil flowing out of the port B of the first one-way valve flows into the second reversing valve through the port B of the second reversing valve, the hydraulic oil flows out of the port A of the second reversing valve after passing through the port A of the motor group, the flushing safety valve group is in a state III, no hydraulic oil flows into the flushing safety valve group at the moment, the hydraulic oil flowing out of the port A of the second reversing valve flows into the motor group through the port A of the motor group, and the hydraulic oil flowing into the motor group from the port A and the port B of the motor group is supplemented for the motor group, and the passive wave compensation motion of the trestle along with the wave fluctuation is realized.
5. The wave compensation type closed rotary hydraulic control system for the marine trestle according to claim 1, characterized in that when the power system of the trestle is unexpectedly powered off, the reversing valve set is powered by a backup battery without failure, the first reversing valve is in a left position, the second reversing valve is in a right position, the third reversing valve is in a right position, the fourth reversing valve is in a left position, the first cartridge valve is in a closed state, the second cartridge valve is in a closed state, hydraulic oil in the accumulator set flows out through an A port of the accumulator set, hydraulic oil flowing out from the A port of the accumulator set flows into the fourth reversing valve through an A port of the fourth reversing valve, hydraulic oil flowing into the fourth reversing valve flows out through a B port of the fourth reversing valve, hydraulic oil flowing out from the B port of the fourth reversing valve flows into the proportional speed regulating valve through an A port of the proportional speed regulating valve, hydraulic oil flowing out from the B port of the proportional speed regulating valve flows into the first one-way valve through the A port of the first one-way valve, the hydraulic oil flows out of the port B of the first one-way valve through the first one-way valve, the hydraulic oil flowing out of the port B of the first one-way valve flows into the motor group through the port B of the motor group, the hydraulic oil flows out of the port A of the variable motor group through the port A of the variable motor group, the hydraulic oil flowing out of the port A of the motor group flows into the first reversing valve through the port A of the first reversing valve, the hydraulic oil directly flows back to the oil tank through the port B of the variable motor group after passing through the first reversing valve, and the reset movement of the trestle system under the condition of accidental power failure is realized under the action of the hydraulic oil in the energy accumulator group.
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