CN114215800A - Rotary damping control hydraulic system - Google Patents
Rotary damping control hydraulic system Download PDFInfo
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- CN114215800A CN114215800A CN202111321353.8A CN202111321353A CN114215800A CN 114215800 A CN114215800 A CN 114215800A CN 202111321353 A CN202111321353 A CN 202111321353A CN 114215800 A CN114215800 A CN 114215800A
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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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/60—Rope, cable, or chain winding mechanisms; Capstans adapted for special purposes
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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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
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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
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
- F15B20/007—Overload
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- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides a rotary damping control hydraulic system, which is used for the lap joint of an offshore trestle and comprises a rotary system, a main oil inlet, a main oil outlet, a main control oil port and an oil tank, wherein the main oil inlet is communicated with the main oil outlet; the rotary system comprises a rotary proportional valve, a first balance valve, a second balance valve, a first shuttle valve, a left hydraulic motor, a right hydraulic motor, a left brake, a right brake, an overflow oil bridge brake valve and an electromagnetic directional valve; according to the invention, when the marine trestle is switched from the follow-up working condition to the normal working condition, the oil paths in the two rotating directions are not communicated, so that the trestle cannot rotate out of control.
Description
Technical Field
The invention relates to the technical field of ship and ocean engineering, in particular to a rotary damping control hydraulic system.
Background
The offshore trestle is important marine equipment, can realize the transportation of personnel and materials under the condition of stormy 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.
However, when the trestle is separated from the lap joint and the rotary system is changed from the follow-up working condition to the normal working condition, the left-turn oil circuit and the right-turn oil circuit of the motor are still in a communicated state, so that the trestle can be out of control in rotation under the influence of waves, and accidents occur.
Disclosure of Invention
The invention provides a rotary damping control hydraulic system, which is characterized in that by using the structure of the invention, when a marine trestle is switched from a follow-up working condition to a normal working condition, the trestle cannot generate the condition of out-of-control rotation.
In order to achieve the purpose, the technical scheme of the invention is as follows: a rotary damping control hydraulic system comprises a rotary system, a main oil inlet, a main oil outlet, a main control oil port and an oil tank; the rotary system comprises a rotary proportional valve, a first balance valve, a second balance valve, a first shuttle valve, a left hydraulic motor, a right hydraulic motor, a left brake, a right brake, an overflow oil bridge brake valve and an electromagnetic directional valve.
A port P of the rotary proportional valve is connected with a main oil inlet, a port T of the rotary proportional valve is connected with an oil tank, a port A of the rotary proportional valve is respectively connected with a port A of the first balance valve and a first oil inlet of the first shuttle valve, and a port B of the rotary proportional valve is respectively connected with a port A of the second balance valve and a second oil inlet of the first shuttle valve; when the rotary proportional valve is positioned at the position a, the port P is communicated with the port B; when the rotary proportional valve is positioned at the middle position, the port A and the port B are respectively communicated with the port T; when the rotary proportional valve is positioned at the position B, the port P is communicated with the port A, and the port B is communicated with the port T.
The port B of the first balance valve is respectively connected with the first oil port of the left hydraulic motor and the first oil port of the right hydraulic motor; and the port B of the second balance valve is respectively connected with the second oil port of the left hydraulic motor and the second oil port of the right hydraulic motor.
A C2 port of the rotary control valve is connected with an oil outlet of the first balance valve, and a C1 port of the rotary control valve is connected with an oil outlet of the second balance valve; the L port of the rotary control valve is respectively connected with the T port of the electromagnetic directional valve and the oil tank, and the T port of the rotary control valve is connected with the oil tank.
The rotary control valve comprises an overflow oil bridge brake valve, a logic valve and a rotary overflow valve.
The overflow oil bridge brake valve comprises a damping overflow valve, a first check valve, a second check valve, a third check valve and a fourth check valve; an oil inlet of the first check valve is connected with the port C1, and an oil outlet of the first check valve is connected with an oil inlet of the damping overflow valve; an oil inlet of the second check valve is connected with the port C2, and an oil outlet of the second check valve is connected with an oil inlet of the damping overflow valve; an oil inlet of the third one-way valve is respectively connected with an oil outlet of the damping overflow valve and a T port of the rotary control valve, and an oil outlet of the third one-way valve is connected with a port C1; an oil inlet of the fourth one-way valve is respectively connected with an oil outlet of the damping overflow valve and a T port of the rotary control valve, and an oil outlet of the fourth one-way valve is connected with a port C2; an oil outlet of the damping overflow valve is connected with a T port of the rotary control valve; an overflow port of the damping overflow valve is connected with an oil inlet of the logic valve, an oil outlet of the logic valve is connected with an oil inlet of the rotary overflow valve, and an oil outlet of the rotary overflow valve is connected with an L port of the rotary control valve; the control oil port of the logic valve is connected with the port B of the electromagnetic directional valve, and the oil drainage port of the logic valve is connected with the port L of the rotary control valve.
A port B of the electromagnetic directional valve is respectively connected with a port PC1 of the rotary control valve and a first oil inlet of the second shuttle valve, and a second oil inlet of the second shuttle valve is connected with an oil inlet of the first shuttle valve; an oil outlet of the second shuttle valve is respectively connected with the left brake and the right brake; the port A of the electromagnetic directional valve is not communicated; the P port of the electromagnetic directional valve is connected with the control oil port.
According to the arrangement, when the offshore trestle is required to be lapped, the rotary system is in a normal working condition, the rotary proportional valve is in a position a or a position B, the port P of the electromagnetic directional valve is communicated with the port A, the port T of the electromagnetic directional valve is communicated with the port B, and the oil circuit of the oil port is controlled not to circulate; hydraulic oil of the main oil inlet enters a port P of the rotary proportional valve, then flows out through a port A or a port B and respectively enters a first balance valve or a second balance valve; meanwhile, the hydraulic oil passes through the first shuttle valve and then the left brake and the right brake are respectively opened; when the pressure of an oil inlet of the damping overflow valve is greater than the set pressure, the hydraulic oil flows out from an overflow port of the damping overflow valve and flows out from an L port of the rotary control valve and returns to the oil tank.
When the landing trestle on the sea is lapped, and a rotary system is switched to a follow-up wave compensation working condition from a normal working condition, the rotary proportional valve is in a middle position, a port P of the electromagnetic directional valve is communicated with a port B, a port A of the electromagnetic directional valve is communicated with a port T, and at the moment, an oil circuit of the control oil port flows in from the port P of the electromagnetic directional valve and flows to a port PC1 of the rotary control valve and a first oil inlet of the second shuttle valve after passing through the port B; the hydraulic oil flows out of an oil outlet of the second shuttle valve and then the left brake and the right brake are respectively opened; hydraulic oil enters a control oil port of the logic valve through the PC1 of the rotary control valve to drive the logic valve to change direction, and a P port of the logic valve is communicated with a T port, namely an overflow port of the damping overflow valve is communicated with an oil tank; at the moment, the left hydraulic motor and the right hydraulic motor continue to rotate under the action of inertia; hydraulic oil flowing out of the left hydraulic motor and the right hydraulic motor enters the first check valve or the second check valve through a C1 port or a C2 port of the overflow oil bridge control valve and enters the damping overflow valve, then the hydraulic oil enters the logic valve from the overflow port and finally enters the rotary overflow valve, the set pressure of the rotary overflow valve is the pressure of the left hydraulic motor and the right hydraulic motor under the following working condition, and when the oil pressure output by the logic valve is greater than the set pressure of the rotary overflow valve, the hydraulic oil flows out of the rotary overflow valve and returns to the oil tank; because the damping overflow valve is used for limiting the pressure, when the pressure of hydraulic oil output by the left hydraulic motor and the right hydraulic motor is greater than the set pressure of the damping overflow valve, the hydraulic oil entering from the oil inlet of the damping overflow valve can flow out of the oil outlet of the damping overflow valve, and then the hydraulic oil respectively flows back to the left hydraulic motor, the right hydraulic motor, the first check valve and the second check valve through the third check valve and the fourth check valve; the oil passages in the two rotation directions of the left hydraulic motor and the right hydraulic motor are communicated, so that the follow-up function is realized; meanwhile, the damping overflow valve limits the pressure of one end of the oil inlet of the damping overflow valve when the oil inlet is communicated with the oil outlet, and when the left hydraulic motor and the right hydraulic motor rotate, constant damping resistance, namely the set pressure of the damping overflow valve, is provided for the left hydraulic motor and the right hydraulic motor.
When the oil pressures of the oil inlets of the left hydraulic motor and the right hydraulic motor are insufficient, the third one-way valve and the fourth one-way valve can suck oil from the oil tank through the T port of the rotary control valve, so that the left hydraulic motor and the right hydraulic motor can be prevented from being damaged by air suction; when the working condition is switched, the rotary control valve can also overflow the oil bridge brake valve to reduce the hydraulic impact in the rotary system, and the brake is stable.
When the trestle needs to be separated from the lap joint, the trestle is changed into a normal working condition from a follow-up working condition again, and a constant damping force is provided for the left hydraulic motor and the right hydraulic motor through the pressure set by the damping overflow valve, so that the left hydraulic motor and the right hydraulic motor are prevented from freely rotating and the out-of-control condition is avoided.
Furthermore, a first reducing valve is connected between the main oil inlet and the P port of the rotary proportional valve, an oil inlet of the first reducing valve is connected with the main oil inlet, and an oil outlet of the first reducing valve is connected with the P port of the rotary proportional valve; an overflow port of the first pressure reducing valve is connected with a pressure reducing shuttle valve, an oil inlet of the pressure reducing shuttle valve is connected with the overflow port of the first pressure reducing valve, a first oil outlet of the pressure reducing shuttle valve is connected with a port A of the rotary proportional valve, and a second oil outlet of the pressure reducing shuttle valve is connected with a port B of the rotary proportional valve; according to the arrangement, the hydraulic oil output by the main oil inlet is decompressed through the first pressure reducing valve, so that the hydraulic impact on the rotary proportional valve is reduced; the hydraulic oil discharged from the overflow port of the first reducing valve returns to the oil tank through the pressure reducing shuttle valve.
Furthermore, a second pressure reducing valve is connected between the electromagnetic directional valve and the control oil port, an oil inlet of the second pressure reducing valve is connected with the control oil port, an oil outlet of the second pressure reducing valve is connected with the P port of the electromagnetic directional valve, and an overflow port of the second pressure reducing valve is connected with the L port of the rotary control valve; through the arrangement, when the rotary system is in a follow-up working condition, the control oil port inputs hydraulic oil to the electromagnetic directional valve through the second pressure reducing valve, and the second pressure reducing valve reduces hydraulic impact on the electromagnetic directional valve.
Furthermore, the first balance valve and the second balance valve are also provided with control oil ports; a control oil port of the first balance valve is connected between the port A of the second balance valve and the second oil inlet of the first shuttle valve; a control oil port of the second balance valve is connected between the port A of the first balance valve and the first oil inlet of the first shuttle valve; above setting, when being in follow-up operating mode, open the control hydraulic fluid port of another balanced valve through a balanced valve respectively between first balanced valve and the second balanced valve to the flow of hydraulic oil backward flow oil tank has been improved.
Furthermore, oil drainage ports of the left hydraulic motor and the right hydraulic motor are connected with an oil tank in parallel.
Further, the left hydraulic motor and the right hydraulic motor are both bidirectional variable motors.
Furthermore, a port B of the electromagnetic directional valve is also connected with a pressure switch; therefore, when the pressure of the rotary system is overlarge, the operation of the rotary system can be quickly stopped through the pressure switch.
Drawings
Fig. 1 is a hydraulic schematic of the present invention.
Fig. 2 is a hydraulic schematic diagram of a rotary control valve according to the present invention.
Fig. 3 is a partially enlarged schematic view of a portion a of fig. 1.
Reference numerals: 11. a rotary proportional valve; 121. a first counter-balance valve; 122. a second balancing valve; 13. a first shuttle valve; 141. a left hydraulic motor; 142. a right hydraulic motor; 151. left braking; 152. a right brake; 16. an overflow oil bridge brake valve; 161. A first check valve; 162. a second one-way valve; 163. a third check valve; 164. a fourth check valve; 165. a damping overflow valve; 17. an electromagnetic directional valve; 18. a rotary overflow valve; 19. a logic valve; 21. a main oil inlet; 22. a main oil outlet; 23. a main control oil port; 3. a rotary control valve.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
As shown in fig. 1-3, a rotary damping control hydraulic system includes a rotary system, a main oil inlet 21, a main oil outlet 22, a main control oil port 23 and an oil tank; the swing system includes a swing proportional valve 11, a first balance valve 121, a second balance valve 122, a first shuttle valve 13, a left hydraulic motor 141, a right hydraulic motor 142, a left brake 151, a right brake 152, a spill oil bridge brake valve 16, and a solenoid directional valve 17.
A port P of the rotary proportional valve 11 is connected with a main oil inlet 21, a port T of the rotary proportional valve 11 is connected with an oil tank, a port A of the rotary proportional valve 11 is respectively connected with a port A of the first balance valve 121 and a first oil inlet of the first shuttle valve 13, and a port B of the rotary proportional valve 11 is respectively connected with a port A of the second balance valve 122 and a second oil inlet of the first shuttle valve 13; when the rotary proportional valve 11 is positioned at the position a, the port P is communicated with the port B; when the rotary proportional valve 11 is positioned at the middle position, the port A and the port B are respectively communicated with the port T; when the rotary proportional valve 11 is positioned at the position B, the port P is communicated with the port A, and the port B is communicated with the port T.
The B port of the first balance valve 121 is connected to the first oil port of the left hydraulic motor 141 and the first oil port of the right hydraulic motor 142, respectively; the B ports of the second balance valve 122 are connected to the second port of the left hydraulic motor 141 and the second port of the right hydraulic motor 142, respectively.
A port C2 of the rotary control valve is connected with an oil outlet of the first balance valve 121, and a port C1 of the rotary control valve is connected with an oil outlet of the second balance valve 122; the L port of the rotary control valve is respectively connected with the T port of the electromagnetic directional valve 17 and the oil tank, and the T port of the rotary control valve is connected with the oil tank.
The swing control valve includes a spill bridge brake valve 16, a logic valve 19, and a swing spill valve 18.
The spill oil bridge brake valve 16 includes a damping spill valve 165, a first check valve 161, a second check valve 162, a third check valve 163, and a fourth check valve 164; an oil inlet of the first check valve 161 is connected with a port C1, and an oil outlet of the first check valve 161 is connected with an oil inlet of the damping overflow valve 165; an oil inlet of the second check valve 162 is connected with the port C2, and an oil outlet of the second check valve 162 is connected with an oil inlet of the damping overflow valve 165; an oil inlet of the third check valve 163 is respectively connected with an oil outlet of the damping overflow valve 165 and a T port of the rotary control valve, and an oil outlet of the third check valve 163 is connected with a C1 port; an oil inlet of the fourth check valve 164 is respectively connected with an oil outlet of the damping overflow valve 165 and a T port of the rotary control valve, and an oil outlet of the fourth check valve 164 is connected with a C2 port; an oil outlet of the damping overflow valve 165 is connected with a T port of the rotary control valve; an overflow port of the damping overflow valve 165 is connected with an oil inlet of the logic valve 19, an oil outlet of the logic valve 19 is connected with an oil inlet of the rotary overflow valve 18, and an oil outlet of the rotary overflow valve 18 is connected with an L port of the rotary control valve; the control oil port of the logic valve 19 is connected with the port B of the electromagnetic directional valve 17, and the oil drainage port of the logic valve 19 is connected with the port L of the rotary control valve.
The port B of the electromagnetic directional valve 17 is respectively connected with the port PC1 of the rotary control valve and the first oil inlet of the second shuttle valve, and the second oil inlet of the second shuttle valve is connected with the oil inlet of the first shuttle valve 13; the oil outlet of the second shuttle valve is respectively connected with a left brake 151 and a right brake 152; the port A of the electromagnetic directional valve 17 is not communicated; the P port of the electromagnetic directional valve 17 is connected with a control oil port.
According to the arrangement, when the offshore trestle is required to be lapped, the rotary system is in a normal working condition, the rotary proportional valve 11 is in a position a or a position B, the port P of the electromagnetic directional valve 17 is communicated with the port A, the port T of the electromagnetic directional valve 17 is communicated with the port B, and at the moment, the oil circuit of the oil port is controlled not to circulate; hydraulic oil in the main oil inlet 21 enters a port P of the rotary proportional valve 11, then flows out through a port A or a port B, and enters a first balance valve 121 or a second balance valve 122 respectively; meanwhile, after the hydraulic oil passes through the first shuttle valve 13, the left brake 151 and the right brake 152 are respectively opened; after flowing out of the first balance valve 121 or the second balance valve 122, the hydraulic oil respectively enters the left hydraulic motor 141 and the right hydraulic motor 142, meanwhile enters the rotary control valve through a port C1 or a port C2 of the rotary control valve, then enters the damping overflow valve 165, and when the pressure at the oil inlet of the damping overflow valve 165 is greater than the set pressure, the hydraulic oil flows out of the overflow port of the damping overflow valve 165 and flows out of a port L of the rotary control valve to return to the oil tank.
When the landing trestle on the sea is lapped, and a rotary system is switched to a follow-up wave compensation working condition from a normal working condition, the rotary proportional valve 11 is in a middle position, a port P of the electromagnetic directional valve 17 is communicated with a port B, a port A of the electromagnetic directional valve 17 is communicated with a port T, and at the moment, an oil path of a control oil port flows in from the port P of the electromagnetic directional valve 17 and respectively flows to a port PC1 of the rotary control valve and a first oil inlet of a second shuttle valve after passing through the port B; after the hydraulic oil flows out of the oil outlet of the second shuttle valve, a left brake 151 and a right brake 152 are respectively opened; hydraulic oil enters a control oil port of the logic valve 19 through the PC1 of the rotary control valve to drive the logic valve 19 to change the direction, and a P port and a T port of the logic valve 19 are communicated, namely an overflow port of the damping overflow valve 165 is communicated with an oil tank; at this time, the left and right hydraulic motors 141 and 142 continue to rotate by inertia; the hydraulic oil flowing out of the left hydraulic motor 141 and the right hydraulic motor 142 enters the first check valve 161 or the second check valve 162 through a C1 port or a C2 port of the overflow oil bridge control valve and enters the damping overflow valve 165, then the hydraulic oil enters the logic valve 19 from an overflow port and finally enters the rotary overflow valve 18, the pressure set by the rotary overflow valve 18 is the pressure of the left hydraulic motor 141 and the right hydraulic motor 142 under the follow-up working condition, and when the oil pressure output by the logic valve 19 is greater than the pressure set by the rotary overflow valve 18, the hydraulic oil flows out of the rotary overflow valve 18 and returns to the oil tank; because the damping overflow valve 165 limits the pressure, when the pressure of the hydraulic oil output by the left hydraulic motor 141 and the right hydraulic motor 142 is greater than the set pressure of the damping overflow valve 165, the hydraulic oil entering from the oil inlet of the damping overflow valve 165 can flow out from the oil outlet of the damping overflow valve 165, and then the hydraulic oil respectively flows back to the left hydraulic motor 141 and the right hydraulic motor 142 and the first check valve 161 and the second check valve 162 through the third check valve 163 and the fourth check valve 164; the oil paths in the two rotation directions of the left hydraulic motor 141 and the right hydraulic motor 142 are communicated, so that the follow-up function is realized; meanwhile, the damping overflow valve 165 limits the pressure at one end of the oil inlet of the damping overflow valve 165 while the oil inlet and the oil outlet are communicated, and provides constant damping resistance, i.e., the pressure set by the damping overflow valve 165, for the left hydraulic motor 141 and the right hydraulic motor 142 when the left hydraulic motor 141 and the right hydraulic motor 142 rotate.
When the oil pressure at the oil inlets of the left hydraulic motor 141 and the right hydraulic motor 142 is insufficient, the third check valve 163 and the fourth check valve 164 can suck oil from the oil tank through the T port of the rotary control valve, so that the damage of the left hydraulic motor 141 and the right hydraulic motor 142 due to air suction can be prevented; when the working condition is switched, the rotary control valve can also overflow the oil bridge brake valve 16 to reduce the hydraulic impact in the rotary system, and the brake is stable.
When the trestle needs to be separated from the lap joint, the working condition is changed from the follow-up working condition to the normal working condition again, and a constant damping force is provided for the left hydraulic motor 141 and the right hydraulic motor 142 through the pressure set by the damping overflow valve 165, so that the left hydraulic motor 141 and the right hydraulic motor 142 are prevented from freely rotating and being out of control.
A first reducing valve is connected between the main oil inlet 21 and the port P of the rotary proportional valve 11, an oil inlet of the first reducing valve is connected with the main oil inlet 21, and an oil outlet of the first reducing valve is connected with the port P of the rotary proportional valve 11; an overflow port of the first pressure reducing valve is connected with a pressure reducing shuttle valve, an oil inlet of the pressure reducing shuttle valve is connected with the overflow port of the first pressure reducing valve, a first oil outlet of the pressure reducing shuttle valve is connected with a port A of the rotary proportional valve 11, and a second oil outlet of the pressure reducing shuttle valve is connected with a port B of the rotary proportional valve 11; according to the arrangement, the hydraulic oil output from the main oil inlet 21 is decompressed through the first pressure reducing valve, so that the hydraulic impact on the rotary proportional valve 11 is reduced; the hydraulic oil discharged from the overflow port of the first reducing valve returns to the oil tank through the pressure reducing shuttle valve.
A second reducing valve is also connected between the electromagnetic directional valve 17 and the control oil port, the oil inlet of the second reducing valve is connected with the control oil port, the oil outlet of the second reducing valve is connected with the P port of the electromagnetic directional valve 17, and the overflow port of the second reducing valve is connected with the L port of the rotary control valve; with the above arrangement, when the rotary system is in the follow-up working condition, the control oil port inputs hydraulic oil to the electromagnetic directional valve 17 through the second pressure reducing valve, and the second pressure reducing valve reduces hydraulic impact on the electromagnetic directional valve 17.
The first balance valve 121 and the second balance valve 122 are also provided with control oil ports; the control oil port of the first balance valve 121 is connected between the port a of the second balance valve 122 and the second oil inlet of the first shuttle valve 13; the control oil port of the second balance valve 122 is connected between the port a of the first balance valve 121 and the first oil inlet of the first shuttle valve 13; with the above arrangement, when the hydraulic oil tank is in a follow-up working condition, the control oil port of the other balance valve is opened between the first balance valve 121 and the second balance valve 122 through the one balance valve, so that the flow rate of the hydraulic oil flowing back to the oil tank is increased.
The oil discharge ports of the left hydraulic motor 141 and the right hydraulic motor 142 are connected in parallel to an oil tank.
The left hydraulic motor 141 and the right hydraulic motor 142 are both bidirectional variable motors.
The port B of the electromagnetic directional valve 17 is also connected with a pressure switch; therefore, when the pressure of the rotary system is overlarge, the operation of the rotary system can be quickly stopped through the pressure switch.
The control method of the slewing damping control hydraulic system comprises the following steps:
(1) when the offshore trestle is required to be lapped, when the rotary system is in a normal working condition, the port P of the electromagnetic directional valve 17 is communicated with the port A, the port T of the electromagnetic directional valve 17 is communicated with the port B, and the oil way of the control oil port is not circulated at the moment.
(2) The rotary proportional valve 11 is controlled to be switched to a position or b position according to the requirement of left-hand or right-hand turning.
(3) After the offshore trestle is lapped, the rotary system is switched to a follow-up working condition, the electromagnetic directional valve 17 is controlled to change direction, at the moment, the port P of the electromagnetic directional valve 17 is communicated with the port B, and the port A of the electromagnetic directional valve 17 is communicated with the port T; while the rotary proportional valve 11 is switched to the neutral position.
(4) When the trestle needs to be separated from the lap joint, the rotary system is switched to a normal working condition from a follow-up working condition, and the hydraulic oil flowing out from the oil outlet of the damping overflow valve 165 cannot flow out from the third check valve 163 and the fourth check valve 164, so that the oil paths in the two rotation directions of the left hydraulic motor 141 and the right hydraulic motor 142 are disconnected, and the left hydraulic motor 141 and the right hydraulic motor 142 are prevented from being out of control.
Claims (7)
1. The utility model provides a gyration damping control hydraulic system for marine landing stage overlap joint, its characterized in that: the oil tank comprises a rotary system, a main oil inlet, a main oil outlet, a main control oil port and an oil tank; the rotary system comprises a rotary proportional valve, a first balance valve, a second balance valve, a first shuttle valve, a left hydraulic motor, a right hydraulic motor, a left brake, a right brake, an overflow oil bridge brake valve and an electromagnetic directional valve;
a port P of the rotary proportional valve is connected with a main oil inlet, a port T of the rotary proportional valve is connected with an oil tank, a port A of the rotary proportional valve is respectively connected with a port A of the first balance valve and a first oil inlet of the first shuttle valve, and a port B of the rotary proportional valve is respectively connected with a port A of the second balance valve and a second oil inlet of the first shuttle valve; when the rotary proportional valve is positioned at the position a, the port P is communicated with the port B; when the rotary proportional valve is positioned at the middle position, the port A and the port B are respectively communicated with the port T; when the rotary proportional valve is positioned at the position B, the port P is communicated with the port A, and the port B is communicated with the port T;
the port B of the first balance valve is respectively connected with the first oil port of the left hydraulic motor and the first oil port of the right hydraulic motor; the port B of the second balance valve is respectively connected with the second oil port of the left hydraulic motor and the second oil port of the right hydraulic motor;
a C2 port of the rotary control valve is connected with an oil outlet of the first balance valve, and a C1 port of the rotary control valve is connected with an oil outlet of the second balance valve; an L port of the rotary control valve is respectively connected with a T port of the electromagnetic directional valve and an oil tank, and the T port of the rotary control valve is connected with the oil tank;
the rotary control valve comprises an overflow oil bridge brake valve, a logic valve and a rotary overflow valve;
the overflow oil bridge brake valve comprises a damping overflow valve, a first check valve, a second check valve, a third check valve and a fourth check valve; an oil inlet of the first check valve is connected with the port C1, and an oil outlet of the first check valve is connected with an oil inlet of the damping overflow valve; an oil inlet of the second check valve is connected with the port C2, and an oil outlet of the second check valve is connected with an oil inlet of the damping overflow valve; an oil inlet of the third one-way valve is respectively connected with an oil outlet of the damping overflow valve and a T port of the rotary control valve, and an oil outlet of the third one-way valve is connected with a port C1; an oil inlet of the fourth one-way valve is respectively connected with an oil outlet of the damping overflow valve and a T port of the rotary control valve, and an oil outlet of the fourth one-way valve is connected with a port C2; an oil outlet of the damping overflow valve is connected with a T port of the rotary control valve; an overflow port of the damping overflow valve is connected with an oil inlet of the logic valve, an oil outlet of the logic valve is connected with an oil inlet of the rotary overflow valve, and an oil outlet of the rotary overflow valve is connected with an L port of the rotary control valve; the control oil port of the logic valve is connected with the port B of the electromagnetic directional valve, and the oil drainage port of the logic valve is connected with the port L of the rotary control valve;
a port B of the electromagnetic directional valve is respectively connected with a port PC1 of the rotary control valve and a first oil inlet of the second shuttle valve, and a second oil inlet of the second shuttle valve is connected with an oil inlet of the first shuttle valve; an oil outlet of the second shuttle valve is respectively connected with the left brake and the right brake; the port A of the electromagnetic directional valve is not communicated; the P port of the electromagnetic directional valve is connected with the control oil port.
2. A rotary damping control hydraulic system according to claim 1, characterized in that: a first reducing valve is connected between the main oil inlet and the P port of the rotary proportional valve, the oil inlet of the first reducing valve is connected with the main oil inlet, and the oil outlet of the first reducing valve is connected with the P port of the rotary proportional valve; an overflow port of the first pressure reducing valve is connected with a pressure reducing shuttle valve, an oil inlet of the pressure reducing shuttle valve is connected with the overflow port of the first pressure reducing valve, a first oil outlet of the pressure reducing shuttle valve is connected with a port A of the rotary proportional valve, and a second oil outlet of the pressure reducing shuttle valve is connected with a port B of the rotary proportional valve.
3. A rotary damping control hydraulic system according to claim 1, characterized in that: a second pressure reducing valve is further connected between the electromagnetic directional valve and the control oil port, the oil inlet of the second pressure reducing valve is connected with the control oil port, the oil outlet of the second pressure reducing valve is connected with the P port of the electromagnetic directional valve, and the overflow port of the second pressure reducing valve is connected with the L port of the rotary control valve.
4. A rotary damping control hydraulic system according to claim 1, characterized in that: the first balance valve and the second balance valve are also provided with control oil ports; a control oil port of the first balance valve is connected between the port A of the second balance valve and the second oil inlet of the first shuttle valve; and a control oil port of the second balance valve is connected between the port A of the first balance valve and the first oil inlet of the first shuttle valve.
5. A rotary damping control hydraulic system according to claim 1, characterized in that: the oil drainage ports of the left hydraulic motor and the right hydraulic motor are connected with an oil tank in parallel.
6. A rotary damping control hydraulic system according to claim 1, characterized in that: the left hydraulic motor and the right hydraulic motor are both bidirectional variable motors.
7. A rotary damping control hydraulic system according to claim 1, characterized in that: the port B of the electromagnetic directional valve is also connected with a pressure switch.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111321353.8A CN114215800A (en) | 2021-11-09 | 2021-11-09 | Rotary damping control hydraulic system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111321353.8A CN114215800A (en) | 2021-11-09 | 2021-11-09 | Rotary damping control hydraulic system |
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| CN114215800A true CN114215800A (en) | 2022-03-22 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114215801A (en) * | 2021-11-09 | 2022-03-22 | 中船华南船舶机械有限公司 | Control method for rotary damping control hydraulic system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114215801A (en) * | 2021-11-09 | 2022-03-22 | 中船华南船舶机械有限公司 | Control method for rotary damping control hydraulic system |
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