CN108412822B - Position compensation telescopic boarding trestle rotation hydraulic system and working method - Google Patents

Position compensation telescopic boarding trestle rotation hydraulic system and working method Download PDF

Info

Publication number
CN108412822B
CN108412822B CN201711237395.7A CN201711237395A CN108412822B CN 108412822 B CN108412822 B CN 108412822B CN 201711237395 A CN201711237395 A CN 201711237395A CN 108412822 B CN108412822 B CN 108412822B
Authority
CN
China
Prior art keywords
rotary
valve
way
hydraulic
output end
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201711237395.7A
Other languages
Chinese (zh)
Other versions
CN108412822A (en
Inventor
陈懿
王江
梁兆环
郭安罗
李新献
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
South China Marine Machinery Co Ltd
Original Assignee
South China Marine Machinery Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by South China Marine Machinery Co Ltd filed Critical South China Marine Machinery Co Ltd
Priority to CN201711237395.7A priority Critical patent/CN108412822B/en
Publication of CN108412822A publication Critical patent/CN108412822A/en
Application granted granted Critical
Publication of CN108412822B publication Critical patent/CN108412822B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01D—CONSTRUCTION OF BRIDGES, ELEVATED ROADWAYS OR VIADUCTS; ASSEMBLY OF BRIDGES
    • E01D15/00—Movable or portable bridges; Floating bridges
    • E01D15/24—Bridges or similar structures, based on land or on a fixed structure and designed to give access to ships or other floating structures
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The invention discloses a position compensation telescopic boarding trestle rotary hydraulic system and a working method thereof, wherein the position compensation telescopic boarding trestle rotary hydraulic system comprises a power system and a rotary hydraulic system; the power system comprises a hydraulic oil tank, a main pump group and a high-low pressure pump group; the rotary hydraulic system comprises a rotary selection valve, a rotary direction speed control valve, a rotary brake control valve, a rotary mode selection valve, a rotary balance valve I, a rotary balance valve II, a rotary two-way direction valve, a rotary sequence valve, a rotary hydraulic motor and a rotary brake. The working method is that the active driving, the active compensation and the follow-up of the rotary hydraulic system are realized by controlling the selector valve, the rotary direction speed control valve, the rotary brake control valve and the rotary mode selector valve. By utilizing the hydraulic system and the working method, the rotary hydraulic system can realize active driving, active compensation and zero displacement follow-up compensation.

Description

Position compensation telescopic boarding trestle rotation hydraulic system and working method
Technical Field
The invention relates to a retractable landing trestle rotary hydraulic system.
Background
Walking bridges or trestles are mainly used for transporting people or goods, and on land, the construction of walking bridges is relatively simple, but the walking bridges used on the sea for transporting people and goods between two ships are relatively difficult to construct, because the ships move with each other, the walking bridges are generally constructed on one ship, and if the walking bridges are needed to be used, the walking bridges are arranged between the two ships in an overlapping mode. In the lapping process, the relative position between the walking bridge and another ship needs to be considered for realizing better lapping, otherwise, the walking bridge collides with the ship due to the floating of the ship; after the lap joint is finished, the relative positions of the two ships are also required to be considered, and the walking bridge is in a passive compensation state according to the relative positions of the two ships, so that the normal use can be ensured; in addition, in case of emergency, the walking bridge and another ship can be separated from each other in an emergency, so that the safety performance is ensured.
The patent document with Chinese patent application number 201510045917.8 discloses a step bridge device, include the base and install the rotary platform of base top, rotary platform pass through rotation mechanism with the base is connected, be provided with the driver's cabin on the rotary platform, rotary platform is connected with the step bridge, the both sides of step bridge have safety barrier, the suspension end of step bridge is provided with interfacing apparatus. Compared with the prior art, the marine platform has reasonable structural arrangement and stable operation, and can realize the transportation of personnel between the ship and the marine platform in a complex and severe environment. Although the above-described bridge device is capable of transporting persons and materials between ships, after the bridge device is lapped and the bridge device is lapped, the bridge device cannot be subjected to corresponding position change according to the position change between the ships, and thus, there are problems such as accidents and the like, and in an emergency, the bridge device cannot be separated from the bridge device in an emergency.
The Chinese patent application No. 200610049538.7 discloses a fully hydraulic driven boarding ladder, which comprises a main ladder composed of a ladder frame fixed on a wharf and provided with a running ladder, and an auxiliary ladder capable of moving to a deck surface of a ship and provided with a triangular ladder and a gangway ladder, wherein the auxiliary ladder is composed of a slide, a variable-amplitude rotating mechanism, a hydraulic station, a travelling wheel device and a lifting mechanism fixed on the wharf, the travelling wheel device on the slide is lifted along an I-steel guide rail on the ladder frame by a lifting oil cylinder, a rotating platform on the slide rotates around a central shaft on a horizontal plane, the front end of the rotating platform is hinged with the gangway ladder, the gangway ladder rotates on a vertical plane around a support on the rotating platform by the expansion and contraction of the variable-amplitude oil cylinder, the heights of the triangular ladder and the gangway ladder are adjusted, the rotating oil cylinder rotates the gangway in a 120-degree range of the horizontal plane, the hydraulic station, the variable-amplitude rotating mechanism are all in, the device has the advantages of compact structure, simplified oil path, reduced oil pipe, safe and reliable use, good working synchronization stability and high sensitivity, and is particularly suitable for meeting the requirement of large drop change on oil products and chemical wharfs. Although the structure has certain advantages, the ship runs or stops on water, due to the influence of a plurality of factors, the ship can rise, sink, shake and the like, so that great trouble is brought to the lap joint, and after the lap joint, if the auxiliary ladder cannot be followed, the boarding ladder is easy to damage, and people can not pass and materials can not be conveyed stably.
The patent document with Chinese patent application number 201611205250.4 discloses a three-degree-of-freedom wave compensation boarding trestle, which adopts the technical scheme that: it includes: the device comprises a base platform, a control system, an attitude sensor, a trestle support, a trestle channel, a luffing cylinder and a rolling compensation cylinder; although the invention can realize real-time compensation of the rolling, pitching and heaving motions of the ship, how to control the amplitude-variable oil cylinder and the rolling compensation oil cylinder is not recorded in the technical scheme, the technical scheme realizes active compensation, when the trestle channel is well lapped, the control system is required to control the amplitude-variable oil cylinder and needs a certain reaction time, so that the phenomenon of delay control is easy to occur, the energy consumption is high, the weight of the trestle channel is heavy, and when the trestle channel is well lapped, most of the weight of the trestle channel falls on the lapping point.
The Chinese patent application No. 201610396070.2 discloses a boarding device and a method with a wave compensation function in the fields of marine transportation and marine ship operation, wherein before boarding, a gangway ladder is perpendicular to a deck and is fixedly connected with a gangway ladder support, a motion controller firstly controls an active wave compensation platform to compensate rolling, pitching and heaving of a ship in real time, then controls a motor to rotate reversely, the motor drives a steel wire rope to release the gangway ladder, the gangway ladder rotates anticlockwise around a universal joint, and when a gangway ladder angle sensor detects that the gangway ladder rotates to a preset angle relative to an upper platform in a releasing way, the motor stops operating; after the boarding is finished, the motion controller controls the motor to rotate forwards, when the gangway ladder angle sensor detects that the gangway ladder rotates to a preset angle relative to the upper platform, the gangway ladder is perpendicular to the deck, and the gangway ladder is fixed on the gangway ladder support; the wave compensation platform compensates the rolling, pitching and heaving of the ship in real time in severe sea conditions, the automatic folding and unfolding gangway ladder is folded and unfolded when the upper platform is compensated to a certain stable state, and the stability and the safety during boarding are improved. This structure is through the position of initiative wave compensation regulation platform, then realizes the overlap joint, and because boats and ships are rocked, is difficult to guarantee the position between gangway ladder and the boats and ships at the overlap joint in-process, and the overlap joint is very difficult, and after the overlap joint, if the gangway ladder can not realize the follow-up, then damage this structure easily, also can not carry out steady passerby and transport the goods and materials.
Disclosure of Invention
The invention aims to provide a position compensation telescopic boarding trestle rotary hydraulic system and a working method.
In order to achieve the aim, the position compensation telescopic boarding trestle rotary hydraulic system comprises a power system and a rotary hydraulic system;
the power system comprises a hydraulic oil tank, a main pump set and a high-low pressure pump set, wherein the input end of the main pump set is connected to the hydraulic oil tank, the main pump set is provided with an output end, the input end of the high-low pressure pump set is connected to the hydraulic oil tank, and the high-low pressure pump set is respectively provided with a low-pressure output end and a high-pressure output end; an oil return pipeline is connected to the hydraulic oil tank; an oil unloading pipeline is connected to the hydraulic oil tank;
the rotary hydraulic system comprises a rotary selection valve, a rotary direction speed control valve, a rotary brake control valve, a rotary mode selection valve, a rotary balance valve I, a rotary balance valve II, a rotary two-way direction valve, a rotary sequence valve, a rotary hydraulic motor and a rotary brake; the output end of the main pump set is connected to the input end of a rotary selector valve through a one-way valve, the output end of the rotary selector valve is connected to the input end of a rotary direction speed control valve, the output end A of the rotary direction speed control valve is connected to one end of a rotary hydraulic motor through a rotary one-way valve, the output end B of the rotary direction speed control valve is connected to one end of a rotary two-way direction valve through a rotary one-way valve II, and the output end of the rotary one-way valve I is connected with the other end of the rotary two-way direction valve; the input end of the rotary brake control valve is connected to the output end of the rotary selector valve, and the output end of the rotary brake control valve is connected to the rotary brake through a rotary hydraulic control reversing valve; the input end of the rotary mode selection valve is connected with the output end of the rotary selection valve, the output end of the rotary mode selection valve is connected with the control end of the rotary two-way direction valve through a rotary sequence valve, and the output end of the rotary mode selection valve is connected with the control end of the rotary hydraulic motor; one end of the first rotary balance valve is connected with the output end of the first rotary one-way valve, and the output end of the first rotary balance valve is connected with the oil return pipeline; the input end of the second rotary balance valve is connected with the output end of the second rotary check valve, and the output end of the second rotary balance valve is connected with the oil return pipeline.
The working method of the position compensation telescopic boarding trestle rotary hydraulic system comprises the following steps: after the main pump set is started, the main pump set pumps hydraulic oil out of the hydraulic oil tank to the output end of the main pump set; when the rotary mode selection valve is controlled to be in a normal mode, the rotary brake control valve is controlled to be in a closed state, and the rotary direction speed control valve is in an open state, the rotary selection valve is opened according to a left-turn or right-turn signal received by the rotary direction speed control valve, hydraulic oil at the output end of the main pump set enters the rotary selection valve through the one-way valve I, the hydraulic oil is input to the rotary direction speed control valve, the rotary brake control valve and the rotary mode selection valve through the output end of the rotary selection valve, the hydraulic oil reaches the control end of the rotary two-way direction valve through the rotary mode selection valve and the rotary hydraulic control sequence valve, the rotary two-way direction valve is controlled to be closed, the hydraulic oil enters the rotary brake through the rotary brake control valve and the rotary reversing valve, the rotary brake is closed, meanwhile, the hydraulic oil enters the rotary hydraulic motor from the rotary direction speed control valve to drive the rotary, returning oil of the rotary hydraulic motor enters an oil return pipeline from the first rotary balance valve or the second rotary balance valve;
in the steps, the main pump set continuously supplies oil to realize active driving, and after the rotating direction speed control valve receives a changing signal, the rotating direction speed control valve can rotate the left rotation or the right rotation of the rotating hydraulic motor according to the signal, and can control the rotating speed, so that the active compensation function is realized.
When the rotary mode selection valve is in a follow-up mode, the control end of the rotary two-way directional valve unloads oil, the rotary two-way directional valve resets and is opened, the rotary two-way directional valve communicates the oil inlet and the oil outlet of the rotary hydraulic motor, zero displacement is achieved, and the rotary hydraulic motor is in a follow-up state.
Furthermore, the rotary selector valve comprises a rotary two-position two-way electromagnetic valve and a rotary logic valve, one end of the rotary two-position two-way electromagnetic valve is connected with the oil unloading pipeline, and the other end of the rotary two-position two-way electromagnetic valve is connected with the control end of the rotary logic valve; the one-way valve is connected to the input end of the rotary logic valve, and the output end of the rotary logic valve is connected to the input end of the rotary direction speed control valve. When the rotary two-position two-way electromagnetic valve has no signal, the rotary logic valve is closed, and when the rotary two-position two-way electromagnetic valve has an opening signal, the rotary two-position two-way electromagnetic valve is opened, and the rotary logic valve is controlled to be opened by the rotary two-position two-way electromagnetic valve, so that the selection of whether the rotation is opened or not is realized. Thus, whether the swing is turned on or not can be reliably selected.
Furthermore, the rotation direction speed control valve comprises a rotation electric proportional pressure reducing valve and a rotation three-position four-way hydraulic control reversing valve, and the rotation electric proportional pressure reducing valve is connected to the control end of the rotation three-position four-way hydraulic control reversing valve; the output end of the rotary selector valve is connected to the input end of the rotary three-position four-way hydraulic control reversing valve, the rotary three-position four-way hydraulic control reversing valve is connected with the oil return pipeline, and the rotary three-position four-way hydraulic control reversing valve is provided with output ends A and B. When the rotary electric proportional pressure reducing valve receives the signal, the rotary electric proportional pressure reducing valve is opened and opened according to the signal, and the rotary three-position four-way hydraulic control reversing valve is controlled by the rotary electric proportional pressure reducing valve, so that the left turn or the right turn of the rotary hydraulic motor is realized. In the structure, if the rotary electric proportional pressure reducing valve receives a left-turn signal, the left-turn rotary electric proportional pressure reducing valve is opened, the left-turn rotary electric proportional pressure reducing valve controls the rotary three-position four-way hydraulic control reversing valve, hydraulic oil output from the output end of the rotary selector valve is output from the output end B through the rotary three-position four-way hydraulic control reversing valve and then enters the rotary hydraulic motor through the rotary one-way valve II, return oil of the rotary hydraulic motor returns to an oil return pipeline through the rotary balance valve, and certain damping can be provided for the return oil due to the arrangement of the rotary balance valve I, so that the rotary hydraulic motor rotates stably. If the rotary electric proportional pressure reducing valve receives a right-turn signal, the right-turn rotary electric proportional pressure reducing valve is opened, the right-turn rotary electric proportional pressure reducing valve controls the rotary three-position four-way hydraulic control reversing valve, hydraulic oil output from the output end of the rotary selector valve is output from the output end A through the rotary three-position four-way hydraulic control reversing valve and then enters the rotary hydraulic motor through the first rotary check valve, return oil of the rotary hydraulic motor returns to an oil return pipeline through the second rotary balance valve, and due to the arrangement of the second rotary balance valve, certain damping can be given to the return oil, and therefore the rotary hydraulic motor rotates stably.
Furthermore, a rotary pressure reducing valve is arranged between the rotary selector valve and the input end of the rotary three-position four-way hydraulic control reversing valve. Because the rotary reducing valve is arranged, the pressure of the hydraulic oil entering the rotary three-position four-way hydraulic control reversing valve is stable.
Furthermore, the rotary brake valve comprises a rotary check valve III and a rotary two-position three-way electromagnetic valve I, the output of the rotary selector valve is connected to the rotary check valve III through a rotary overflow pressure reducing valve, the output end of the rotary check valve III is connected to the input end of the rotary two-position three-way electromagnetic valve I, the other input end of the rotary two-position three-way electromagnetic valve I is connected with an oil return pipeline, and the output end of the rotary two-position three-way electromagnetic valve I is connected to the rotary hydraulic control reversing valve. When the first rotary two-position three-way electromagnetic valve is controlled to be in a closed state, hydraulic oil enters the rotary brake through the third rotary one-way valve, the first rotary two-position three-way electromagnetic valve and the rotary hydraulic reversing valve, and the rotary brake is closed; when the first rotary two-position three-way electromagnetic valve is controlled to be in an open state, hydraulic oil input to the first rotary two-position three-way electromagnetic valve is stopped, hydraulic oil of the rotary brake is discharged through the first rotary hydraulic reversing valve and the first rotary two-position three-way electromagnetic valve, and the rotary brake is opened. In the present invention, the brake off means that the brake applies force to the motor, and the brake on means that the brake applies force to the motor by the spring after oil is discharged.
Furthermore, the rotary mode selection valve is a rotary two-position three-way electromagnetic valve II. The selection of the rotation mode is realized by controlling a second rotation two-position three-way electromagnetic valve, and the specific method comprises the following steps: controlling a rotary two-position three-way electromagnetic valve II to be in a normal mode, wherein hydraulic oil output from a rotary selection valve controls a rotary two-way directional valve through the rotary two-position three-way electromagnetic valve II and a rotary sequence valve, the rotary two-way directional valve is closed, and the hydraulic oil on two sides of the rotary two-way directional valve is not communicated so as to realize manual control and active compensation of rotation; and controlling the second rotary two-position three-way electromagnetic valve to be in a follow-up mode, stopping hydraulic oil output from the rotary selector valve at the second rotary two-position three-way electromagnetic valve, discharging the hydraulic oil connected to the control end of the rotary two-way directional valve, and communicating the hydraulic oil on two sides of the rotary two-way directional valve to realize zero-displacement rotary follow-up compensation.
Furthermore, a rotary brake pressure stabilizing energy accumulator is arranged between the rotary hydraulic control reversing valve and the rotary brake. Stable braking pressure is provided for the rotary brake through the rotary brake pressure stabilizing energy accumulator, so that the brake is more reliable and stable.
Furthermore, a second one-way valve is connected to the low-pressure output end, one path of the output end of the second one-way valve is connected to the output end of the second one-way valve through a fourth rotary one-way valve, and the other path of the output end of the second one-way valve is connected to the output end of the first rotary one-way valve through a fifth rotary one-way valve. The rotary hydraulic motor is subjected to quantitative low-pressure oil supplement through the low-pressure output end, and the phenomenon that hydraulic oil of the rotary hydraulic motor is sucked to be empty to cause cavitation in the rotary follow-up process is prevented.
Drawings
Fig. 1 is a schematic view of a first structure of a position compensation telescopic boarding trestle.
Fig. 2 is a downward schematic view of a first structure of the position-compensated telescopic boarding trestle.
Fig. 3 is a schematic view of a second structure of the position compensation telescopic boarding trestle.
Fig. 4 is a downward schematic view of a second configuration of the position compensated telescopic landing stage.
Fig. 5 is an enlarged view of the direction C in fig. 3.
Fig. 6 is an enlarged view of a direction a in fig. 1.
Fig. 7 is an enlarged view of B in fig. 6.
Fig. 8 is a side view of fig. 7.
Fig. 9 is an enlarged view of D in fig. 1.
FIG. 10 is a schematic view of a landing gear.
FIG. 11 is a schematic diagram of a position compensation control system.
FIG. 12 is a schematic diagram of a position compensated hydraulic system.
FIG. 13 is a schematic diagram of a main power system.
FIG. 14 is a schematic diagram of a swing hydraulic system, a telescopic hydraulic system, and an emergency hydraulic system.
FIG. 15 is a schematic view of a rotary hydraulic system.
Fig. 16 is a schematic diagram of a telescopic hydraulic system.
FIG. 17 is a schematic view of a luffing hydraulic system.
Fig. 18 is a schematic view of an accumulator on-off valve.
Fig. 19 is a schematic view of a vacuum emergency hydraulic system.
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 to 6, the position compensation retractable landing trestle comprises a base 11, a rotary platform 12, a retractable trestle 13, a landing device 14, a rotary hydraulic motor 10, a luffing cylinder 20, a position compensation control system 4 and a position compensation hydraulic system 5.
As shown in fig. 9, the swing platform 12 includes an inner ring gear 121 rotatably mounted on the base 11, a swing drive gear 122 mounted on an output shaft of the swing hydraulic motor 10, and a swing seat 123 fixed on the inner ring gear 121, the swing hydraulic motor 10 being mounted on the base 11. The number of the rotary hydraulic motors 10 is two or more. The accommodating cavity 1231 is formed in the rotary seat 123, and can be used for placing hydraulic systems such as a control system and a hydraulic oil tank, so that the space can be effectively utilized, and the size of the position compensation telescopic boarding trestle can be reduced.
As shown in fig. 1 to 4, a base maintenance platform 15 is installed on the base 11, so that a maintenance worker can conveniently stand on the base maintenance platform 15 for maintenance. A base ladder 16 is fixed on the base 11, a passage ladder 17 is connected to the upper end of the base ladder 16, and the passage ladder 17 leads to the platform of the revolving bed 123. The cab 18 is mounted on the swivel base 123.
As shown in fig. 1 to 6, the telescopic trestle 13 includes a main arm 131 and a telescopic arm 132. The main arm 131 is an aluminum alloy frame, and the telescopic arm 132 is an aluminum alloy frame, so that the whole telescopic trestle is light in weight, and consumes little energy in the amplitude variation process. One end of the main arm 131 is hinged to the rotary seat 123, and a guardrail 1311 is arranged on the main arm 131, so that the guardrail can play a role in protection when people pass. In the present invention, the telescopic arm 132 is slidably disposed on the main arm 131, since the main arm 131 and the telescopic arm 132 are made of an aluminum alloy material, although the main arm 131 and the telescopic arm 132 have a light weight and relatively low strength and wear resistance, in order to accommodate the sliding of the telescopic arm 132, the main arm 132 is provided with the steel guide rail 133, the steel guide rail 133 has high strength and good wear resistance, and the steel guide rails 133 are disposed at upper and lower positions in the main arm 131. The aluminum alloy and the steel are in direct contact, and the anode corrosion phenomenon is easy to occur, so the aluminum alloy structure and the steel guide rail adopt an insulation fixing device 134 structure: as shown in fig. 7 and 8, the insulating fixing device 134 includes a lower pressing plate 1341, an upper pressing plate 1342, a screw assembly 1343 and a rubber pad 1344; a rubber pad 1344 is arranged on the upper surface of the lower pressing plate 1341, a rubber pad 1344 is arranged on the lower surface of the upper pressing plate 1342, and a square tube in the main arm is clamped between the two rubber pads 1344; the screw assembly comprises a screw, a nut and a washer, the screw assembly penetrates through the upper pressing plate 1341, the lower pressing plate 1342 and the rubber pad 1344 to clamp one square pipe of the main arm, and a gap is reserved between the screw assembly and the corresponding square pipe of the main arm, so that the screw assembly is prevented from contacting with the main arm; the steel guide rail is arranged on the lower pressing plate and/or the upper pressing plate, the aluminum alloy and the steel guide rail are insulated by arranging the rubber pad, anode corrosion is avoided, and the aluminum alloy main arm and the telescopic arm are better protected.
As shown in fig. 5 and 6, a first roller set 135 contacting the upper steel rail 133 is provided on the upper side of the telescopic arm 132, a second roller set 136 contacting the lower steel rail 133 is provided on the lower side of the telescopic arm 132, a bracket 137 is provided on the upper side of the telescopic arm 132, and a third roller set 138 contacting the upper steel rail 133 is provided on the bracket 137 in a lateral direction. As shown in fig. 1 to 4, the first roller group 135 includes a first bracket 1351 mounted on the telescopic arm and a first roller 1352 provided on the first bracket 1351, and the first roller 1352 is a rubber roller. The second roller set 136 includes a second bracket 1361, a swing arm 1362 and a second roller 1363, the second bracket 1361 is fixed on the telescopic arm 132, the middle part of the swing arm 1362 is hinged on the second bracket 1361, the two ends of the swing arm 1362 are respectively provided with the second roller 1363, and the second roller 1363 is a rubber roller. The third roller group comprises third brackets 1381 arranged at two sides of the brackets and third rollers 1382 arranged on the third brackets 1381. A fourth pulley block 139 is arranged in the free end of the main arm 131, and the fourth pulley block 139 comprises a fourth support 1391 mounted on the main arm and a fourth pulley arranged on the fourth support 1391; the left and right sides of the inner side of the free end of the main arm are respectively provided with a fifth pulley block 1310. When the telescopic boom 132 extends out, the fourth pulley block 139 can resist the first and second pulley blocks to prevent the telescopic boom from sliding out of the main boom; because the first pulley block, the third pulley block, the fourth pulley block and the fifth pulley block are arranged, the telescopic resistance of the telescopic boom is small, and the telescopic boom operates stably. And the third pulley, the fourth pulley and the fifth pulley in the fifth pulley block are rubber pulleys.
And when the telescopic boom stroke limit sensors detect that the telescopic boom reaches a limit position, the telescopic boom stops moving.
A telescopic driving means including a telescopic hydraulic motor 20, a telescopic driving gear 21, and a telescopic driving rack 22 is provided between the main arm 131 and the telescopic arm 132. The telescopic hydraulic motor 20 is installed on the main arm 131, the telescopic driving gear 21 is installed on an output shaft of the telescopic hydraulic motor, the telescopic driving rack 22 is installed on the telescopic arm 132, the telescopic driving gear 21 is meshed with the telescopic driving rack 22, and when the telescopic hydraulic motor 20 works, the telescopic gear 21 rotates to drive the telescopic driving rack 22 to move linearly and drive the telescopic arm 132 to extend or retract.
A telescopic support rod 1311 is attached to the main arm 132 to support the main arm 132 and to be telescopic according to the swing angle of the main arm.
A ladder 1312 is mounted at the free end of the telescopic arm 132.
As shown in fig. 1, 3 and 10, the landing gear 14 is mounted at the free end of the telescopic arm, and includes a support 141, a ball head mounted on the support 141, and a support plate 142 movably linked with the ball head. This structure, after flexible landing stage 13 overlap joint to the overlap joint point, supporting disc 142 with by the lapped platform contact to through coupling mechanism with supporting disc 142 with by the overlap joint platform be connected, when there is position change by the overlap joint platform, because the effect of bulb, can give certain swing buffering space, only need consider like this gyration, flexible and become the width of cloth compensation can, need not consider other swing angles except that the width of cloth angle, simplified the compensation design.
As shown in fig. 1 and 3, one end of the luffing cylinder 30 is hinged to the swivel base 123, and the other end of the luffing cylinder 30 is hinged to the main arm 131.
As shown in fig. 3 and 4, another structure of the position compensating telescopic boarding trestle is that a base elevating mechanism 19 is installed on a base 11. The base lifting mechanism 19 comprises a fixing sleeve 191 fixed on the deck 100, a lifting oil cylinder 192 hinged on the deck 100 and a lifting column 193, wherein the lifting column 193 is fixed on the base 11, the lower end of the lifting column 193 is inserted into the fixing sleeve 191, and the upper end of the lifting oil cylinder 192 is hinged on the base 11. The lifting oil cylinder is used for controlling the base to ascend or descend; the specific method comprises the following steps: a piston rod of the lifting oil cylinder moves upwards, the lifting oil cylinder pushes the base, the rotary platform and the telescopic trestle to move upwards together, the lifting column moves on the fixing sleeve, and the movement of the lifting column is guided through the fixing sleeve; if the piston rod of the lifting oil cylinder moves downwards, the base, the rotary platform and the telescopic trestle are driven to move downwards, and therefore the purpose of adjusting the upper and lower positions of the base, the rotary platform and the telescopic trestle is achieved.
A lifting locking mechanism is arranged between the fixed sleeve 191 and the lifting column 193, the lifting locking mechanism comprises a locking oil cylinder 194 arranged on the fixed sleeve and a jack 195 arranged on the lifting column, and a piston rod of the locking oil cylinder 194 can be matched with the jack 195. And starting the locking oil cylinder, wherein a piston rod of the locking oil cylinder can be inserted into the jack to lock the lifting column, starting the locking oil cylinder in the direction, and separating the piston rod of the locking oil cylinder from the jack to unlock the lifting column. Therefore, the lifting column can be locked and loosened, and if a lifting base is not needed, the lifting column can be more reliably connected with the fixed sleeve through the locking mechanism.
An oil and/or water delivery pipe 1000 which penetrates through the main arm 131 and is connected to the telescopic arm is connected to the base 11, the oil and/or water delivery pipe on the main arm can be a hose or a hard pipe, and the hose on the telescopic arm. Therefore, water and oil can be conveniently conveyed to the free end of the telescopic trestle, and the water and oil can also be conveyed to the lapped platform.
As shown in fig. 11, the position compensation control system 4 includes an industrial personal computer 41, an MRU sensor 42, a DP system 43, a decoder 44, an operating handle 45, a cab button 46, a cab touch screen 47, and a light alarm 48.
Install MRU sensor respectively on the free end of flexible arm and by overlap joint platform or boats and ships, the MUR sensor is connected with the industrial computer, the DP system is connected with the industrial computer through this platform and by the control room on the overlap joint platform, the decoder includes decoder one and decoder two, be connected with operating handle on the decoder one, connect wireless remote controller on the decoder two, the decoder is connected with the industrial computer, the driver's cabin button is connected with the industrial computer, driver's cabin touch-sensitive screen 47, light alarm 48 is connected with the industrial computer respectively, industrial computer 41 is connected with position compensation hydraulic system 5.
The industrial personal computer is connected with a smoke alarm, a gas detection sensor, a hydraulic oil low-level sensor, a hydraulic oil excessively low-level sensor, a hydraulic height sensor, a hydraulic oil temperature sensor, a wind speed sensor, a system pressure sensor, a rotary limit sensor, a telescopic boom stroke limit sensor, a variable amplitude angle sensor and a camera system. After the corresponding sensor detects a signal, the signal is displayed on a touch screen of the cab or an alarm is given out through a light alarm, so that the safety performance is improved.
As shown in fig. 12, the position compensating hydraulic system 5 includes a power system 51, a slewing hydraulic system 52, a telescopic hydraulic system 53, a luffing hydraulic system 54, and an emergency hydraulic system 55.
As shown in fig. 13, the power system 51 includes a hydraulic oil tank 511, a main pump group 512, and a high-low pressure pump group 513. In this embodiment, main pump group 512 is provided with two sets ofly, and main pump group 512 drives through main pump motor 514 respectively, and main pump motor 514 is connected to the industrial computer to supply power through transmission line. A low hydraulic switch 515, a low hydraulic switch 516 and a temperature switch 517 are connected to the hydraulic oil tank 511; the main pump group 512 is respectively connected with a main pump unloading valve 518; a system pressure protection system 519 is connected to the main pump group 512; the main pump group 512 has an input connected to the hydraulic oil tank 511 and the main pump group 512 has an output 5121. The input end of the high-low pressure pump set 513 is connected to the hydraulic oil tank 511, the high-low pressure pump set 513 comprises a high-pressure pump and a low-pressure pump, the high-pressure pump and the low-pressure pump are driven by the same motor 5110, the motor 5110 is connected with an industrial personal computer, and meanwhile, the motor 5110 is powered by a power supply circuit; the low pressure pump has a low pressure output 5131 and the high pressure pump has a high pressure output 5132; an oil return pipeline 5113 is connected to the hydraulic oil tank 511 through a filter 5112; an oil discharge line 5114 is connected to the hydraulic oil tank 511.
As shown in fig. 14 and 15, the swing hydraulic system 52 includes a swing selector valve 521, a swing direction speed control valve 522, a swing brake control valve 523, a swing mode selector valve 524, a swing trim valve 525, a swing trim valve 526, a swing two-way direction valve 527, a swing sequence valve 528, a swing hydraulic motor 10, and a swing brake 529.
The output ends of the main pump groups are gathered into a whole through a one-way valve I56. And a main system pressure sensor is arranged at the output end of the one-way valve I56.
The rotary selector valve 521 comprises a rotary two-position two-way electromagnetic valve and a rotary logic valve, one end of the rotary two-position two-way electromagnetic valve is connected with the oil unloading pipeline DR, and the other end of the rotary two-position two-way electromagnetic valve is connected with the control end of the rotary logic valve; one-way valve one 56 is connected to the input of the rotary logic valve, the output of which is connected to the input of the rotary direction speed control valve. When the rotary two-position two-way electromagnetic valve has no signal, the rotary logic valve is closed, and when the rotary two-position two-way electromagnetic valve has an opening signal, the rotary two-position two-way electromagnetic valve is opened, and the rotary logic valve is controlled to be opened by the rotary two-position two-way electromagnetic valve, so that the selection of whether the rotation is opened or not is realized. Thus, whether the swing is turned on or not can be reliably selected.
The rotation direction speed control valve 522 comprises a rotation electric proportional pressure reducing valve and a rotation three-position four-way hydraulic control reversing valve, and the rotation electric proportional pressure reducing valve is connected to the control end of the rotation three-position four-way hydraulic control reversing valve; the output end of the rotary selector valve is connected to the input end of a rotary three-position four-way hydraulic control reversing valve, the rotary three-position four-way hydraulic control reversing valve is connected with the oil return pipeline DR, and the rotary three-position four-way hydraulic control reversing valve is provided with output ends A and B; the industrial personal computer is connected to the rotary electric proportional pressure reducing valve. When the rotary electric proportional pressure reducing valve receives the signal, the rotary electric proportional pressure reducing valve controls the rotary three-position four-way hydraulic control reversing valve according to the opening size of the signal, and the left turn or the right turn of the rotary hydraulic motor is realized. In the structure, if the rotary electric proportional pressure reducing valve receives a left-turn signal, the left-turn rotary electric proportional pressure reducing valve is opened, the left-turn rotary electric proportional pressure reducing valve controls the rotary three-position four-way hydraulic control reversing valve, hydraulic oil output from the output end of the rotary selector valve is output from the output end B through the rotary three-position four-way hydraulic control reversing valve and then enters the rotary hydraulic motor through the rotary one-way valve II, return oil of the rotary hydraulic motor returns to an oil return pipeline through the rotary balance valve, and certain damping can be provided for the return oil due to the arrangement of the rotary balance valve I, so that the rotary hydraulic motor rotates stably. If the rotary electric proportional pressure reducing valve receives a right-turn signal, the right-turn rotary electric proportional pressure reducing valve is opened, the right-turn rotary electric proportional pressure reducing valve controls the rotary three-position four-way hydraulic control reversing valve, hydraulic oil output from the output end of the rotary selector valve is output from the output end A through the rotary three-position four-way hydraulic control reversing valve and then enters the rotary hydraulic motor through the first rotary check valve, return oil of the rotary hydraulic motor returns to an oil return pipeline through the second rotary balance valve, and due to the arrangement of the second rotary balance valve, certain damping can be given to the return oil, and therefore the rotary hydraulic motor rotates stably.
And a rotary reducing valve is arranged between the rotary selector valve and the input end of the rotary three-position four-way hydraulic control reversing valve. Because the rotary reducing valve is arranged, the pressure of the hydraulic oil entering the rotary three-position four-way hydraulic control reversing valve is stable.
And a rotary system pressure sensor is arranged between the output end of the rotary logic valve and the rotary pressure reducing valve.
The rotary brake valve comprises a rotary check valve III and a rotary two-position three-way electromagnetic valve I, the output of the rotary selector valve is connected to the rotary check valve III through a rotary overflow pressure reducing valve, the output end of the rotary check valve III is connected to the input end of the rotary two-position three-way electromagnetic valve I, the other input end of the rotary two-position three-way electromagnetic valve I is connected with an oil return pipeline, the output end of the rotary two-position three-way electromagnetic valve I is connected to the rotary brake 529 through a rotary hydraulic control reversing valve 5210, and the output end of the rotary hydraulic control reversing valve 5210 is connected. When the first rotary two-position three-way electromagnetic valve is controlled to be in a closed state, hydraulic oil enters the rotary brake through the third rotary one-way valve, the first rotary two-position three-way electromagnetic valve and the rotary hydraulic reversing valve, and the rotary brake is closed; when the first rotary two-position three-way electromagnetic valve is controlled to be in an open state, hydraulic oil input to the first rotary two-position three-way electromagnetic valve is stopped, hydraulic oil of the rotary brake is discharged through the first rotary hydraulic reversing valve and the first rotary two-position three-way electromagnetic valve, and the rotary brake is opened. In the present invention, the brake off means that the brake applies force to the motor, and the brake on means that the brake applies force to the motor by the spring after oil is discharged. And a control signal of the first rotary two-position three-way electromagnetic valve is from an industrial personal computer.
The input end of the rotary mode selection valve is connected with the output end of the rotary selection valve, the output end of the rotary mode selection valve is connected with the control end of the rotary two-way direction valve through a rotary sequence valve, and the output end of the rotary mode selection valve is connected with the control end of the rotary hydraulic motor; the rotary mode selection valve is a rotary two-position three-way electromagnetic valve II. And the output end of the second rotary two-position three-way electromagnetic valve is connected with a rotary motor displacement control pressure sensor. The selection of the rotation mode is realized by controlling a second rotation two-position three-way electromagnetic valve, and the specific method comprises the following steps: controlling a rotary two-position three-way electromagnetic valve II to be in a normal mode, wherein hydraulic oil output from a rotary selection valve controls a rotary two-way directional valve through the rotary two-position three-way electromagnetic valve II and a rotary sequence valve, the rotary two-way directional valve is closed, and the hydraulic oil on two sides of the rotary two-way directional valve is not communicated so as to realize manual control and active compensation of rotation; and controlling the second rotary two-position three-way electromagnetic valve to be in a follow-up mode, stopping hydraulic oil output from the rotary selector valve at the second rotary two-position three-way electromagnetic valve, discharging the hydraulic oil connected to the control end of the rotary two-way directional valve, and communicating the hydraulic oil on two sides of the rotary two-way directional valve to realize zero-displacement rotary follow-up compensation.
A rotary brake pressure stabilizing energy accumulator 5211 is arranged between the rotary hydraulic control reversing valve 5210 and the rotary brake 529. Stable braking pressure is provided for the rotary brake through the rotary brake pressure stabilizing energy accumulator, so that the brake is more reliable and stable.
The output end A of the rotary three-position four-way hydraulic control reversing valve is connected to one end of a rotary hydraulic motor 10 through a rotary one-way valve I, the output end B of the rotary three-position four-way hydraulic control reversing valve is connected to one end of a rotary two-way directional valve through a rotary one-way valve II, and the output end of the rotary one-way valve I is connected with the other end of a rotary two-way directional valve 527; one end of the first rotary balance valve is connected with the output end of the first rotary one-way valve, and the output end of the first rotary balance valve is connected with the oil return pipeline; the input end of the second rotary balance valve is connected with the output end of the second rotary check valve, and the output end of the second rotary balance valve is connected with the oil return pipeline.
As shown in fig. 14 and 16, the telescopic hydraulic system 53 includes a telescopic selector valve 531, a telescopic direction speed control valve 532, a telescopic brake control valve 533, a telescopic mode selector valve 534, a telescopic balance valve one 535, a telescopic balance valve two 536, a telescopic two-way direction valve 537, a telescopic sequence valve 538, a telescopic hydraulic motor 20, and a telescopic brake 539.
The telescopic selection valve 531 comprises a telescopic two-position two-way electromagnetic valve and a telescopic logic valve, one end of the telescopic two-position two-way electromagnetic valve is connected with the oil unloading pipeline, and the other end of the telescopic two-position two-way electromagnetic valve is connected with the control end of the telescopic logic valve; one-way valve one 56 is connected to the input of the telescoping logic valve, the output of which is connected to the input of the telescoping direction speed control valve. When the telescopic two-position two-way electromagnetic valve has no signal, the telescopic logic valve is closed, and when the telescopic two-position two-way electromagnetic valve has an opening signal, the telescopic two-position two-way electromagnetic valve is opened, and the telescopic logic valve is controlled to be opened by the telescopic two-position two-way electromagnetic valve, so that the selection of whether the telescopic valve is opened or not is realized. Thus, whether the telescopic mechanism is opened or not can be reliably selected.
The telescopic direction speed control valve comprises a telescopic electric proportional pressure reducing valve and a telescopic three-position four-way hydraulic control reversing valve, and the telescopic electric proportional pressure reducing valve is connected to the control end of the telescopic three-position four-way hydraulic control reversing valve; the output end of the telescopic selection valve is connected to the input end of the telescopic three-position four-way hydraulic control reversing valve, the telescopic three-position four-way hydraulic control reversing valve is connected with the oil return pipeline, and the telescopic three-position four-way hydraulic control reversing valve is provided with output ends A and B; the industrial personal computer is connected to the telescopic electric proportional pressure reducing valve. When the telescopic electric proportional pressure reducing valve receives a signal, the telescopic electric proportional pressure reducing valve is opened and opened according to the signal, the telescopic three-position four-way hydraulic control reversing valve is controlled by the telescopic electric proportional pressure reducing valve, and the left turn or the right turn of the telescopic hydraulic motor is realized. In the structure, if the telescopic electric proportional pressure reducing valve receives an extending signal, the extending telescopic electric proportional pressure reducing valve is opened, the extending telescopic electric proportional pressure reducing valve controls the telescopic three-position four-way hydraulic control reversing valve, hydraulic oil output from the output end of the telescopic selector valve is output from the output end B through the telescopic three-position four-way hydraulic control reversing valve, then enters the telescopic hydraulic motor through the telescopic one-way valve II, oil return of the telescopic hydraulic motor returns to an oil return pipeline through the telescopic balance valve, and certain damping can be given to the oil return due to the arrangement of the telescopic balance valve I, so that the telescopic hydraulic motor rotates stably. If the telescopic electric proportional pressure reducing valve receives a retracting signal, the retracted telescopic electric proportional pressure reducing valve is opened, the retracted telescopic electric proportional pressure reducing valve controls the telescopic three-position four-way hydraulic control reversing valve, hydraulic oil output from the output end of the telescopic selector valve is output from the output end A through the telescopic three-position four-way hydraulic control reversing valve and then enters the telescopic hydraulic motor through the telescopic one-way valve I, oil return of the telescopic hydraulic motor returns to an oil return pipeline through the telescopic balance valve II, and due to the arrangement of the telescopic balance valve II, certain damping can be given to the oil return, and therefore the telescopic hydraulic motor rotates stably.
And a telescopic reducing valve is arranged between the telescopic selection valve and the input end of the telescopic three-position four-way hydraulic control reversing valve. Due to the arrangement of the telescopic reducing valve, the pressure of the hydraulic oil entering the telescopic three-position four-way hydraulic control reversing valve is stable.
And a telescopic system pressure sensor is arranged between the telescopic logic valve and the telescopic three-position four-way hydraulic control reversing valve.
The telescopic brake valve comprises a telescopic one-way valve III and a telescopic two-position three-way electromagnetic valve I, the output of the telescopic selection valve is connected to the telescopic one-way valve III through a telescopic overflow pressure reducing valve, the output end of the telescopic one-way valve III is connected to the input end of the telescopic two-position three-way electromagnetic valve I, the other input end of the telescopic two-position three-way electromagnetic valve I is connected with an oil return pipeline, the output end of the telescopic two-position three-way electromagnetic valve I is connected to the telescopic hydraulic control reversing valve 5310, the telescopic hydraulic control reversing valve 5310 is connected to the telescopic brake 539, and a telescopic brake pressure sensor is arranged between the. When the first telescopic two-position three-way electromagnetic valve is controlled to be in a closed state, hydraulic oil enters the telescopic brake through the third telescopic one-way valve, the first telescopic two-position three-way electromagnetic valve and the telescopic hydraulic reversing valve, and the telescopic brake is closed; when the first telescopic two-position three-way electromagnetic valve is controlled to be in an open state, hydraulic oil input to the first telescopic two-position three-way electromagnetic valve is stopped, hydraulic oil of the telescopic brake is discharged through the first telescopic hydraulic reversing valve and the first telescopic two-position three-way electromagnetic valve, and the telescopic brake is opened. And a control signal of the first telescopic two-position three-way electromagnetic valve is from an industrial personal computer.
The input end of the telescopic mode selection valve is connected with the output end of the telescopic selection valve, the output end of the telescopic mode selection valve is connected with the control end of a telescopic two-way directional valve 537 through a telescopic sequence valve, and the output end of the telescopic mode selection valve is connected with the control end of a telescopic hydraulic motor; the telescopic mode selection valve is a telescopic two-position three-way electromagnetic valve II, and the output end of the telescopic two-position two-way electromagnetic valve II is connected with a telescopic motor displacement control pressure sensor. The selection of the telescopic mode is realized by controlling a telescopic two-position three-way electromagnetic valve II, and the specific method comprises the following steps: controlling the second telescopic two-position three-way electromagnetic valve to be in a normal mode, wherein hydraulic oil output from the telescopic selection valve controls the two-way telescopic directional valve through the second telescopic two-position three-way electromagnetic valve and the telescopic sequence valve, the two-way telescopic directional valve is closed, and the hydraulic oil on the two sides of the two-way telescopic directional valve is not communicated so as to realize manual telescopic control and active compensation; and controlling the second telescopic two-position three-way electromagnetic valve to be in a follow-up mode, stopping the hydraulic oil output from the telescopic selection valve at the second telescopic two-position three-way electromagnetic valve, discharging the hydraulic oil connected to the control end of the two-way telescopic directional valve, and communicating the hydraulic oil on two sides of the two-way telescopic directional valve to realize zero-displacement telescopic follow-up compensation.
And a telescopic brake pressure stabilizing energy accumulator 5311 is arranged between the first telescopic hydraulic control reversing valve and the telescopic brake. The telescopic brake pressure stabilizing energy accumulator provides stable brake pressure for the telescopic brake, so that the brake is more reliable and stable.
The output end A of the telescopic three-position four-way hydraulic control reversing valve is connected to one end of a telescopic hydraulic motor through a telescopic one-way valve I, the output end B of the telescopic three-position four-way hydraulic control reversing valve is connected to one end of a telescopic two-way directional valve through a telescopic one-way valve II, and the output end of the telescopic one-way valve I is connected with the other end of the telescopic two-way directional valve; the input end of the first telescopic balance valve 535 is connected with the output end of the first telescopic one-way valve 535, and the output end of the first telescopic balance valve 535 is connected with the oil return pipeline; the input end of the second telescopic balance valve 536 is connected with the output end of the second telescopic one-way valve, and the output end of the second telescopic balance valve 536 is connected with an oil return pipeline; the industrial personal computer is connected with the telescopic selection valve, the telescopic direction speed control valve, the telescopic brake control valve and the telescopic mode selection valve.
The oil discharge port of the telescopic hydraulic motor 20 is connected with an oil collecting tank, and the telescopic hydraulic motor is arranged on the main arm, so that the distance between the telescopic hydraulic motor and the hydraulic oil tank is long, hydraulic oil can be better collected by arranging the oil collecting tank, and the hydraulic oil can be conveyed into the hydraulic oil tank.
The low-pressure output end is connected with a second check valve 57, one path of the output end of the second check valve 57 is connected to the output end of the second rotary check valve through a fourth rotary check valve 5213, and the other path of the output end of the second check valve 57 is connected to the output end of the first rotary check valve through a fifth rotary check valve 5214. The rotary hydraulic motor is subjected to quantitative low-pressure oil supplement through the low-pressure output end, and the phenomenon that hydraulic oil of the rotary hydraulic motor is sucked to be empty to cause cavitation in the rotary follow-up process is prevented. One path of the output end of the second one-way valve 57 is connected to the output end of the second telescopic one-way valve through a fourth telescopic one-way valve 5313, and the other path of the output end of the second one-way valve is connected to the output end of the first rotary one-way valve through a fifth telescopic one-way valve 5314. The oil is quantitatively supplemented to the telescopic hydraulic motor through the low-pressure output end, so that the phenomenon of cavitation caused by the fact that hydraulic oil of the telescopic hydraulic motor is sucked to be empty in the telescopic follow-up process is prevented.
As shown in fig. 17, the variable amplitude hydraulic system 54 is provided with two sets, and an amplitude-variable rodless cavity oil-connecting valve 547 is arranged between the amplitude-variable oil cylinders of the two sets of variable amplitude hydraulic systems. The amplitude-variable hydraulic system comprises an amplitude-variable selection valve 541, an amplitude-variable direction speed control valve 542, an amplitude-variable energy accumulator control valve 543, an amplitude-variable energy accumulator switch valve 544, an amplitude-variable energy accumulator oil-charging control valve 545, a plunger type energy accumulator 546 and an amplitude-variable oil cylinder 30.
The input end of the variable amplitude selection valve is connected to the output end of the main pump group through a one-way valve, the output end of the variable amplitude selection valve is connected to the input end of the variable amplitude direction speed control valve, the output end A of the variable amplitude direction speed control valve is connected to one end of the variable amplitude oil cylinder through a variable amplitude one-way valve, and the output end B of the variable amplitude direction speed control valve is connected to the other end of the variable amplitude oil cylinder; the variable-amplitude energy accumulator control valve is connected with one end of the variable-amplitude oil cylinder through a second variable-amplitude one-way valve, the variable-amplitude energy accumulator control valve is simultaneously connected with a variable-amplitude energy accumulator switching valve, the variable-amplitude energy accumulator switching valve is connected with a connecting point formed by the second variable-amplitude one-way valve and the variable-amplitude oil cylinder, the input end of the variable-amplitude energy accumulator oil-filling control valve is connected with the output end of the main pump group, the output end of the variable-amplitude energy accumulator oil-filling control valve is connected with the plunger type energy accumulator, the plunger type energy accumulator is connected with the energy accumulator switching valve, and the plunger type energy accumulator is connected; the industrial personal computer is connected with the amplitude-variable selection valve, the amplitude-variable direction speed control valve, the amplitude-variable energy accumulator switch valve and the amplitude-variable energy accumulator oil-charging control valve.
The variable amplitude selection valve 541 comprises a variable amplitude two-position two-way electromagnetic valve and a variable amplitude logic valve, wherein one end of the variable amplitude two-position two-way electromagnetic valve is connected with the oil unloading pipeline, and the other end of the variable amplitude two-position two-way electromagnetic valve is connected with the control end of the variable amplitude logic valve; the first check valve 56 is connected to the input of the luffing logic valve, the output of which is connected to the input of the luffing direction speed control valve. When the amplitude-variable two-position two-way electromagnetic valve has no signal, the amplitude-variable logic valve is closed, and when the amplitude-variable two-position two-way electromagnetic valve has an opening signal, the amplitude-variable two-position two-way electromagnetic valve is opened, and the amplitude-variable logic valve is controlled to be opened by the amplitude-variable two-way electromagnetic valve, so that the selection of whether the amplitude is opened or not is realized.
The amplitude-variable direction speed control valve 542 comprises an amplitude-variable electric proportional pressure reducing valve and an amplitude-variable three-position four-way hydraulic control reversing valve, and the amplitude-variable electric proportional pressure reducing valve is connected to the control end of the amplitude-variable three-position four-way hydraulic control reversing valve; the output end of the amplitude-variable selection valve is connected to the input end of the amplitude-variable three-position four-way hydraulic control reversing valve, the amplitude-variable three-position four-way hydraulic control reversing valve is connected with the oil return pipeline, and the amplitude-variable three-position four-way hydraulic control reversing valve is provided with output ends A and B; the industrial personal computer is connected with the amplitude-variable electric proportional pressure reducing valve. A pressure sensor of the amplitude variation system is arranged between the amplitude variation selection valve and the amplitude variation direction speed control method. When the amplitude-variable electric proportional pressure-reducing valve receives the signal, the amplitude-variable electric proportional pressure-reducing valve is opened and opened according to the signal, and the amplitude-variable three-position four-way hydraulic control reversing valve is controlled by the amplitude-variable electric proportional pressure-reducing valve, so that the motion of the amplitude-variable oil cylinder is realized. In the structure, if the amplitude-variable electric proportional pressure-reducing valve receives a rising signal, the rising amplitude-variable electric proportional pressure-reducing valve is opened, the rising amplitude-variable electric proportional pressure-reducing valve controls the amplitude-variable three-position four-way hydraulic control reversing valve, and hydraulic oil output from the output end of the amplitude-variable selection valve is output into the amplitude-variable oil cylinder from the output end B through the amplitude-variable three-position four-way hydraulic control reversing valve. If the amplitude-variable electric proportional pressure-reducing valve receives a descending signal, the descending amplitude-variable electric proportional pressure-reducing valve is opened, the descending amplitude-variable electric proportional pressure-reducing valve controls the amplitude-variable three-position four-way hydraulic control reversing valve, hydraulic oil output from the output end of the amplitude-variable selection valve is output from the output end A through the amplitude-variable three-position four-way hydraulic control reversing valve, and then enters the amplitude-variable hydraulic motor through the amplitude-variable one-way valve I.
The variable amplitude energy accumulator control valve 543 comprises a variable amplitude two-position three-way electromagnetic valve, a variable amplitude two-position two-way electromagnetic valve I and a variable amplitude two-position two-way electromagnetic valve II. As shown in fig. 18, the accumulator switching valve 544 includes a valve body 5441 and a conical valve core 5442, the conical valve core 5442 is disposed in the valve body 5441, the bottom of the valve body 5441 has a first oil port 5444, a second oil port 5445 is disposed on a side wall of the valve body 5441 near the first oil port 5444, the upper end of the conical valve core 5442 is a piston 5443, a third oil port 5446 is disposed on the valve body 5441 above the piston, a fourth oil port 5447 is disposed on the valve body below the piston, and a spring 5448 is disposed between the piston 5443 and the valve body 5441. One input end of the variable amplitude two-position three-way electromagnetic valve is simultaneously connected with the output ends of the variable amplitude one-way valve II and the variable amplitude one-way valve III, and the output end of the variable amplitude one-way valve is connected with the variable amplitude two-position two-way electromagnetic valve II; the other input end of the variable amplitude two-position three-way electromagnetic valve is respectively communicated with the fourth oil port and connected with the control end of the variable amplitude two-position two-way electromagnetic valve II; the output end of the variable-amplitude two-position two-way electromagnetic valve is connected to a third oil port through a first variable-amplitude two-position two-way electromagnetic valve, and the third oil port is connected with a second variable-amplitude two-position two-way electromagnetic valve; the first oil port is connected with the input end of the variable amplitude one-way valve II; the second oil port is respectively connected with the input end of the variable amplitude one-way valve III and the plunger type energy accumulator; the plunger type energy accumulator is connected with the input end of the variable amplitude one-way valve II through the variable amplitude one-way valve IV. Under the non-follow-up compensation state, the amplitude-variable two-position three-way electromagnetic valve is in a closed state, hydraulic oil of the plunger type energy accumulator enters the upper part of the piston through the amplitude-variable one-way valve III, the amplitude-variable two-position three-way electromagnetic valve, the amplitude-variable two-position two-way electromagnetic valve I and the third oil port, and under the pressure action of the hydraulic oil, the conical valve core blocks the first oil port, namely the switch valve of the amplitude-variable energy accumulator is closed; in the amplitude-variable passive compensation state, the amplitude-variable two-position three-way electromagnetic valve is in an open state, the amplitude-variable energy accumulator switch valve is in an open state, the third oil port and the fourth oil port are communicated with the amplitude-variable two-position two-way electromagnetic valve through the amplitude-variable two-position three-way electromagnetic valve, the amplitude-variable oil cylinder is in a passive state, and constant tension is applied to the amplitude-variable oil cylinder through the plunger type energy accumulator. In a passive compensation state of amplitude variation, if the lapping point has descending traction force, the lapping point pulls the amplitude variation oil cylinder to move, the plunger type energy accumulator gives an ascending constant pressure to the amplitude variation oil cylinder to prevent the telescopic trestle from being overloaded at the lapping point, if the lapping point has ascending traction force, the lapping point pulls the amplitude variation oil cylinder to move, and the plunger type energy accumulator gives an ascending constant pressure to the amplitude variation oil cylinder to prevent the telescopic trestle from being overloaded at the lapping point.
As shown in fig. 19, the emergency hydraulic system employs the following hydraulic system: the high-voltage output end is connected with an energy storage group 583 through an energy storage oil filling valve block 581 and an energy storage control valve block 582 in sequence; the output of accumulator control valve block 582 is connected to the output of check valve one 56. When the output end of the main pump group can not supply oil, the energy accumulator group is filled with oil by controlling the energy accumulator oil filling valve block and the energy accumulator control valve block, and the energy accumulator control valve block supplies oil to the rotary hydraulic system, the telescopic hydraulic system and the variable amplitude hydraulic system through the energy accumulator group, so that emergency oil supply is realized, and the whole system is safe.
The energy storage control valve block comprises an energy storage one-way valve I, an energy storage one-way valve II, an energy storage logic valve, an energy storage two-position two-way electromagnetic directional valve and an energy storage pressure reducing valve; the output end of the energy accumulator oil filling valve is connected to the input end of the energy accumulator one-way valve I, and the output end of the energy accumulator one-way valve I is simultaneously connected with the output ends of the energy accumulator group, the energy accumulator one-way valve II and the input end of the energy accumulator logic valve; the input end of the energy accumulator one-way valve II is connected with the output end of the one-way valve I; the output end of the energy accumulator logic valve is connected to the output end of the first check valve through an energy accumulator pressure reducing valve; one end of the energy accumulator two-position two-way electromagnetic directional valve is connected with an oil unloading pipeline, and the other end of the energy accumulator two-position two-way electromagnetic directional valve is connected with a logic control end of the energy accumulator; when the main pump group can not realize normal oil supply, the two-position two-way electromagnetic directional valve of the energy accumulator is opened, the pressure reducing valve of the energy accumulator is controlled to be opened, and the hydraulic oil of the energy accumulator group supplies oil to the rotary hydraulic system, the telescopic hydraulic system and the amplitude-variable hydraulic system through the logic valve of the energy accumulator and the pressure reducing valve of the energy accumulator. Realize emergent fuel feeding, let entire system safety.
The output end of the pressure reducing valve of the energy accumulator is connected with an energy accumulator for compensating and stabilizing pressure. And oil supply and pressure stabilization of the energy storage device are realized.
The emergency manual control valve is connected to the energy accumulator group through an emergency pipeline, the output end of the emergency manual control valve is divided into two paths, one path is sequentially connected with an emergency brake control valve and a third check valve, and the third check valve is respectively connected with the control ends of the rotary hydraulic control reversing valve and the telescopic hydraulic control reversing valve; the other path is connected with an emergency amplitude-variable lifting manual control valve, the output end of the emergency amplitude-variable lifting manual control valve is divided into two paths, one path is connected to an amplitude-variable energy accumulator control valve, and the other path is connected to an amplitude-variable oil cylinder; if the emergency brake is to be realized, the emergency manual control valve and the emergency brake control valve are opened, the hydraulic oil of the energy accumulator group enters the control ends of the rotary hydraulic control reversing valve and the telescopic hydraulic control reversing valve through the emergency manual control valve, the emergency brake control valve and the one-way valve, and the rotary brake and the telescopic brake unload oil to realize the brake action; if the emergency amplitude-variable lifting is to be realized, the emergency manual control valve and the emergency amplitude-variable lifting manual control valve are opened, and the amplitude-variable oil cylinder is driven by the accumulator group, so that the emergency lifting action is realized. To improve safety performance.
The output end of the emergency amplitude-variable lifting manual control valve is connected with an energy accumulator 584 for emergency amplitude-variable lifting voltage stabilization.
And the output end of the third one-way valve is connected with a voltage stabilizing energy accumulator 585.
The working method of the position compensation telescopic boarding trestle comprises an overlapping method, a follow-up compensation method and a disengagement method;
the lapping method comprises a manual operation lapping method and an active compensation lapping method:
the manual operation lapping method comprises the following steps: an operator operates the operating handle, the decoder decodes a signal of the operating handle and sends the signal to the industrial personal computer, the industrial personal computer controls the starting of the main pump group, and the main pump group pumps hydraulic oil out of the hydraulic oil tank to the output end of the main pump group; the industrial personal computer controls the rotary hydraulic system, the telescopic hydraulic system and the amplitude-variable hydraulic system, the rotary platform is controlled to rotate through the rotary hydraulic system, the telescopic boom is controlled to stretch through the telescopic hydraulic system, the telescopic trestle is controlled to swing through the amplitude-variable hydraulic system, and the telescopic trestle moves to a lap joint range;
the method for controlling the rotation of the rotary platform by the rotary hydraulic system comprises the following steps: the rotary mode selection valve is controlled in a normal mode, the rotary brake control valve is controlled in a closed state, the rotary direction speed control valve selects a left-turn or right-turn state according to a signal of an operating handle, the rotary selection valve is opened, hydraulic oil at the output end of the main pump set enters the rotary selection valve through the one-way valve I, the hydraulic oil is input into the rotary direction speed control valve, the rotary brake control valve and the rotary mode selection valve through the output end of the rotary selection valve, the hydraulic oil reaches the control end of the rotary two-way direction valve through the rotary mode selection valve and the rotary sequence valve to control the closure of the rotary two-way direction valve, the hydraulic oil enters the rotary brake through the rotary brake control valve and the rotary hydraulic control reversing valve to close the rotary brake, and meanwhile, the hydraulic oil enters the rotary hydraulic motor from the rotary direction speed control valve to drive the rotary hydraulic motor to turn left or right so as to control the rotary platform, returning oil of the rotary hydraulic motor enters an oil return pipeline from the first rotary balance valve or the second rotary balance valve;
the method for controlling the telescopic arm to stretch by the telescopic hydraulic system comprises the following steps: the telescopic mode selection valve is controlled in a normal mode, the telescopic brake control valve is controlled in a closed state, the telescopic direction control valve selects an extending state or a retracting state according to a signal of the operating handle, the telescopic selection valve is opened, hydraulic oil at the output end of the main pump set enters the telescopic selection valve through the one-way valve I, the hydraulic oil is input into the telescopic direction speed control valve, the telescopic brake control valve and the telescopic mode selection valve through the output end of the telescopic selection valve, the hydraulic oil reaches the control end of the telescopic two-way direction valve through the telescopic mode selection valve and the telescopic sequence valve to control the closing of the telescopic two-way direction valve, the hydraulic oil enters the telescopic brake through the telescopic brake control valve and the telescopic hydraulic control reversing valve to close the telescopic brake, meanwhile, the hydraulic oil enters the telescopic hydraulic motor from the telescopic direction speed control valve to drive the telescopic hydraulic motor to rotate forwards or reversely, so as to, return oil of the telescopic hydraulic motor enters an oil return pipeline from the first telescopic balance valve or the second telescopic balance valve;
the method for controlling the telescopic trestle to swing by the variable amplitude hydraulic system comprises the following steps: the control valve of the variable-amplitude energy accumulator is controlled to be closed through the industrial personal computer, and the switching valve of the variable-amplitude energy accumulator is controlled to be closed through the industrial personal computer; the amplitude-variable direction control valve selects a rising or falling state according to a signal of the operating handle, the amplitude-variable selection valve is opened, hydraulic oil at the output end of the main pump set enters the amplitude-variable selection valve through the one-way valve I, the hydraulic oil is input to the amplitude-variable direction speed control valve and the amplitude-variable energy accumulator oil-filling control valve through the output end of the amplitude-variable selection valve, and the hydraulic oil enters the amplitude-variable oil cylinder from the amplitude-variable direction speed control valve to drive the telescopic trestle to rise or fall;
when the telescopic trestle moves to the lapping range, the telescopic trestle enters an active compensation lapping state, and the active compensation lapping method comprises the following steps: collecting the position information of the lapping point through an MRU sensor and a DP system, transmitting the position information into an industrial personal computer, calculating in the industrial personal computer, inputting the processed signals to a rotation direction speed control valve, a stretching direction speed control valve and a variable amplitude direction speed control valve, controlling the rotation direction and the speed of a rotation hydraulic motor through the rotation direction speed control valve, controlling the rotation direction and the speed of the stretching hydraulic motor through the stretching direction speed control valve, and controlling the movement direction and the speed of a variable amplitude oil cylinder through the variable amplitude direction speed control valve;
when the lapping of the telescopic trestle is finished, the follow-up compensation is carried out, and the follow-up compensation method comprises a rotation follow-up method, a telescopic follow-up method and a variable amplitude passive compensation method;
the rotation follow-up method comprises the following steps: the rotary mode selection valve is controlled to be in a follow-up mode through an industrial control machine, the control end of the rotary two-way directional valve unloads oil, the rotary two-way directional valve is reset and opened, the rotary two-way directional valve connects an oil inlet and an oil outlet of the rotary hydraulic motor together to realize zero displacement, and the rotary hydraulic motor is in a follow-up state;
the telescopic follow-up method comprises the following steps: the telescopic mode selection valve is controlled to be in a follow-up mode through an industrial personal computer, the control end of the telescopic two-way directional valve unloads oil, the telescopic two-way directional valve is reset and opened, the telescopic two-way directional valve connects an oil inlet and an oil outlet of the telescopic hydraulic motor together to realize zero displacement, and the telescopic hydraulic motor is in a follow-up state;
the amplitude variation passive compensation method comprises the following steps: the amplitude-variable selection valve is controlled to be closed, the amplitude-variable energy accumulator control valve is controlled to be opened, and the amplitude-variable energy accumulator switching valve is controlled to be opened through the industrial control machine; the amplitude-variable oil cylinder is in a passive state, and is in a constant tension mode through the plunger type energy accumulator;
the releasing method is to control the power system, the rotary hydraulic system, the telescopic hydraulic system and the amplitude-variable hydraulic system through the industrial personal computer to release the telescopic trestle.
When an emergency occurs, the emergency hydraulic system is started.
According to the position compensation telescopic boarding trestle and the working method, when the telescopic trestle does not enter the overlapping range, the telescopic trestle can quickly enter the overlapping range through the manual control of the power system, the rotary hydraulic system, the telescopic hydraulic system and the variable amplitude hydraulic system, so that the overlapping efficiency is improved; when flexible landing stage enters into the overlap joint within range, obtain X, Y, Z six orientation's position and corresponding acceleration through the MRU sensor, acquire this platform and by the state of overlap joint platform through the DP system simultaneously, signal transmission who will acquire is to the industrial control built-in, acquire control signal through the calculation, give gyration direction speed control valve respectively, flexible direction speed control valve and become width of cloth direction speed control valve, through controlling gyration direction speed control valve, the reversal and the flow size of flexible direction speed control valve and become width of cloth direction speed control valve come the control gyration hydraulic motor respectively, flexible hydraulic motor and become width of cloth hydro-cylinder, let the free end of flexible landing stage constantly be close to the overlap joint point and follow the gesture by the overlap joint platform and carry out initiative change, let the overlap joint easier, safety and steady. In the invention, the calculation method of the industrial personal computer is the existing calculation method, such as digital PID calculation and the like. After the lapping is finished, the oil inlet and the oil outlet of the rotary hydraulic motor are communicated by controlling the rotary two-way directional valve, and when the traction force of the lapped platform exists, the rotary hydraulic motor can realize follow-up and zero discharge without consuming energy; the oil inlet and the oil outlet of the telescopic hydraulic motor are communicated by controlling the telescopic two-way directional valve, and when the traction force of the lapped platform exists, the telescopic hydraulic motor can realize follow-up and zero discharge without energy consumption; for a variable amplitude hydraulic system, one end of a variable amplitude oil cylinder outputs an oil unloading state, a plunger type energy accumulator is additionally arranged at the other end of the variable amplitude oil cylinder, when the lapped platform has traction force, the variable amplitude oil cylinder realizes passive compensation, and meanwhile, the plunger type energy accumulator always gives a constant tension to the variable amplitude oil cylinder, so that the load of a telescopic trestle on a lapping point is reduced; therefore, after the lapping is completed, the rotary hydraulic motor and the telescopic hydraulic motor realize follow-up along with the position change of the lapped platform, the amplitude-variable oil cylinder realizes passive compensation, the telescopic trestle is stable, and people passing and material transportation are safe and stable. Because the first rotary balance valve and the second rotary balance valve are arranged, a damping is given to the rotary hydraulic motor on an oil return pipeline of the rotary hydraulic motor, so that the rotary hydraulic motor operates stably; similarly, the first telescopic balance valve and the second telescopic balance valve are arranged, so that a damping is given to the first telescopic hydraulic motor on an oil return pipeline of the telescopic hydraulic motor, and the telescopic hydraulic motor is stable in operation. Because the variable amplitude energy accumulator control valve and the variable amplitude energy accumulator switch valve are arranged, in the passive compensation process, the plunger type energy accumulator can be used for providing constant pressure for the variable amplitude oil cylinder, and meanwhile, the passive compensation can be realized. For the main arm and the telescopic arm, the cantilever structure is adopted, so that the weight of the main arm and the telescopic arm needs to be reduced as much as possible in order to improve the stability of the structure, therefore, the aluminum alloy material is selected, but the telescopic arm needs to slide in the main arm, and the aluminum alloy guide rail is adopted, so that the strength and the wear resistance are poor, therefore, the guide rail is made of a steel structure, but the aluminum alloy is in direct contact with the steel structure, so that the anodic corrosion phenomenon is easy to occur, therefore, the rubber pad is arranged to insulate the aluminum alloy guide rail from the steel guide rail, the anodic corrosion is avoided, and the aluminum alloy main arm and the telescopic.

Claims (10)

1. A position compensation telescopic boarding trestle rotary hydraulic system comprises a power system and a rotary hydraulic system; the method is characterized in that:
the power system comprises a hydraulic oil tank, a main pump set and a high-low pressure pump set, wherein the input end of the main pump set is connected to the hydraulic oil tank, the main pump set is provided with an output end, the input end of the high-low pressure pump set is connected to the hydraulic oil tank, and the high-low pressure pump set is respectively provided with a low-pressure output end and a high-pressure output end; an oil return pipeline is connected to the hydraulic oil tank; an oil unloading pipeline is connected to the hydraulic oil tank;
the rotary hydraulic system comprises a rotary selection valve, a rotary direction speed control valve, a rotary brake control valve, a rotary mode selection valve, a rotary balance valve I, a rotary balance valve II, a rotary two-way direction valve, a rotary sequence valve, a rotary hydraulic motor and a rotary brake; the output end of the main pump set is connected to the input end of a rotary selector valve through a one-way valve, the output end of the rotary selector valve is connected to the input end of a rotary direction speed control valve, the output end A of the rotary direction speed control valve is connected to one end of a rotary hydraulic motor through a rotary one-way valve, the output end B of the rotary direction speed control valve is connected to one end of a rotary two-way direction valve through a rotary one-way valve II, and the output end of the rotary one-way valve I is connected with the other end of the rotary two-way direction valve; the input end of the rotary brake control valve is connected to the output end of the rotary selector valve, and the output end of the rotary brake control valve is connected to the rotary brake through a rotary hydraulic control reversing valve; the input end of the rotary mode selection valve is connected with the output end of the rotary selection valve, the output end of the rotary mode selection valve is connected with the control end of the rotary two-way direction valve through a rotary sequence valve, and the output end of the rotary mode selection valve is connected with the control end of the rotary hydraulic motor; one end of the first rotary balance valve is connected with the output end of the first rotary one-way valve, and the output end of the first rotary balance valve is connected with the oil return pipeline; the input end of the second rotary balance valve is connected with the output end of the second rotary check valve, and the output end of the second rotary balance valve is connected with the oil return pipeline.
2. The position-compensating telescopic landing stage slewing hydraulic system according to claim 1, wherein: the rotary selector valve comprises a rotary two-position two-way electromagnetic valve and a rotary logic valve, one end of the rotary two-position two-way electromagnetic valve is connected with the oil unloading pipeline, and the other end of the rotary two-position two-way electromagnetic valve is connected with the control end of the rotary logic valve; the one-way valve is connected to the input end of the rotary logic valve, and the output end of the rotary logic valve is connected to the input end of the rotary direction speed control valve.
3. The position-compensating telescopic landing stage slewing hydraulic system according to claim 1, wherein: the rotation direction speed control valve comprises a rotation electric proportional pressure reducing valve and a rotation three-position four-way hydraulic control reversing valve, and the rotation electric proportional pressure reducing valve is connected to the control end of the rotation three-position four-way hydraulic control reversing valve; the output end of the rotary selector valve is connected to the input end of a rotary three-position four-way hydraulic control reversing valve, the rotary three-position four-way hydraulic control reversing valve is connected with an oil return pipeline, and the rotary three-position four-way hydraulic control reversing valve is provided with output ends A and B; the industrial personal computer is connected to the rotary electric proportional pressure reducing valve.
4. The position compensated telescoping boarding trestle swivel hydraulic system of claim 3, characterized in that: and a rotary reducing valve is arranged between the rotary selector valve and the input end of the rotary three-position four-way hydraulic control reversing valve.
5. The position-compensating telescopic landing stage slewing hydraulic system according to claim 1, wherein: the rotary brake valve comprises a rotary one-way valve III and a rotary two-position three-way electromagnetic valve I, the output of the rotary selector valve is connected to the rotary one-way valve III through a rotary overflow pressure reducing valve, the output end of the rotary one-way valve III is connected to the input end of the rotary two-position three-way electromagnetic valve I, the other input end of the rotary two-position three-way electromagnetic valve I is connected with an oil return pipeline, and the output end of the rotary two-position three-way electromagnetic valve I is connected to the.
6. The position-compensating telescopic landing stage slewing hydraulic system according to claim 1, wherein: the low-pressure output end is connected with a second one-way valve, one path of the output end of the second one-way valve is connected to the output end of the second one-way valve through a fourth one-way rotary valve, and the other path of the output end of the second one-way valve is connected to the output end of the first one-way rotary valve through a fifth one-way rotary valve.
7. A method of operating a position compensated telescopic landing stage slewing hydraulic system as claimed in claim 1, wherein: after the main pump set is started, the main pump set pumps hydraulic oil out of the hydraulic oil tank to the output end of the main pump set; when the rotary mode selection valve is controlled to be in a normal mode, the rotary brake control valve is controlled to be in a closed state, and the rotary direction speed control valve is in an open state, the rotary selection valve is opened according to a left-turn or right-turn signal received by the rotary direction speed control valve, hydraulic oil at the output end of the main pump set enters the rotary selection valve through the one-way valve I, the hydraulic oil is input to the rotary direction speed control valve, the rotary brake control valve and the rotary mode selection valve through the output end of the rotary selection valve, the hydraulic oil reaches the control end of the rotary two-way direction valve through the rotary mode selection valve and the rotary hydraulic control sequence valve, the rotary two-way direction valve is controlled to be closed, the hydraulic oil enters the rotary brake through the rotary brake control valve and the rotary reversing valve, the rotary brake is closed, meanwhile, the hydraulic oil enters the rotary hydraulic motor from the rotary direction speed control valve to drive the rotary, returning oil of the rotary hydraulic motor enters an oil return pipeline from the first rotary balance valve or the second rotary balance valve;
when the rotary mode selection valve is in a follow-up mode, the control end of the rotary two-way directional valve unloads oil, the rotary two-way directional valve resets and is opened, the rotary two-way directional valve communicates the oil inlet and the oil outlet of the rotary hydraulic motor, zero displacement is achieved, and the rotary hydraulic motor is in a follow-up state.
8. The working method of the position compensation retractable landing stage slewing hydraulic system according to claim 7, wherein: the rotary selector valve comprises a rotary two-position two-way electromagnetic valve and a rotary logic valve, one end of the rotary two-position two-way electromagnetic valve is connected with the oil unloading pipeline, and the other end of the rotary two-position two-way electromagnetic valve is connected with the control end of the rotary logic valve; the one-way valve is connected to the input end of the rotary logic valve, and the output end of the rotary logic valve is connected to the input end of the rotary direction speed control valve; when the rotary two-position two-way electromagnetic valve has no signal, the rotary logic valve is closed, and when the rotary two-position two-way electromagnetic valve has an opening signal, the rotary two-position two-way electromagnetic valve is opened, and the rotary logic valve is controlled to be opened by the rotary two-position two-way electromagnetic valve, so that the selection of whether the rotation is opened or not is realized;
the rotation direction speed control valve comprises a rotation electric proportional pressure reducing valve and a rotation three-position four-way hydraulic control reversing valve, and the rotation electric proportional pressure reducing valve is connected to the control end of the rotation three-position four-way hydraulic control reversing valve; the output end of the rotary selector valve is connected to the input end of a rotary three-position four-way hydraulic control reversing valve, the rotary three-position four-way hydraulic control reversing valve is connected with an oil return pipeline, and the rotary three-position four-way hydraulic control reversing valve is provided with output ends A and B; when the rotary electric proportional pressure reducing valve receives a signal, the rotary electric proportional pressure reducing valve is opened and opened according to the signal, and the rotary three-position four-way hydraulic control reversing valve is controlled by the rotary electric proportional pressure reducing valve to realize the left turn or the right turn of the rotary hydraulic motor;
the rotary brake valve comprises a rotary check valve III and a rotary two-position three-way electromagnetic valve I, the output of the rotary selector valve is connected to the rotary check valve III through a rotary overflow pressure reducing valve, the output end of the rotary check valve III is connected to the input end of the rotary two-position three-way electromagnetic valve I, the other input end of the rotary two-position three-way electromagnetic valve I is connected with an oil return pipeline, and the output end of the rotary two-position three-way electromagnetic valve I is connected to the rotary hydraulic control reversing valve; when the first rotary two-position three-way electromagnetic valve is controlled to be in a closed state, hydraulic oil enters the rotary brake through the third rotary one-way valve, the first rotary two-position three-way electromagnetic valve and the rotary hydraulic reversing valve, and the rotary brake is closed; when the first rotary two-position three-way electromagnetic valve is controlled to be in an open state, hydraulic oil input to the first rotary two-position three-way electromagnetic valve is stopped, hydraulic oil of the rotary brake is discharged through the first rotary hydraulic reversing valve and the first rotary two-position three-way electromagnetic valve, and the rotary brake is opened.
9. The working method of the position compensation telescopic boarding trestle gyration hydraulic system according to claim 8, characterized in that: and a rotary reducing valve is arranged between the rotary selector valve and the input end of the rotary three-position four-way hydraulic control reversing valve.
10. The working method of the position compensation retractable landing stage slewing hydraulic system according to claim 1, wherein: the low-pressure output end is connected with a second one-way valve, one path of the output end of the second one-way valve is connected to the output end of the second rotary one-way valve through a fourth rotary one-way valve, and the other path of the output end of the second one-way valve is connected to the output end of the first rotary one-way valve through a fifth rotary one-way valve; the rotary hydraulic motor is supplied with low pressure via a low-pressure output.
CN201711237395.7A 2017-11-30 2017-11-30 Position compensation telescopic boarding trestle rotation hydraulic system and working method Active CN108412822B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201711237395.7A CN108412822B (en) 2017-11-30 2017-11-30 Position compensation telescopic boarding trestle rotation hydraulic system and working method

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201711237395.7A CN108412822B (en) 2017-11-30 2017-11-30 Position compensation telescopic boarding trestle rotation hydraulic system and working method

Publications (2)

Publication Number Publication Date
CN108412822A CN108412822A (en) 2018-08-17
CN108412822B true CN108412822B (en) 2020-01-14

Family

ID=63125309

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201711237395.7A Active CN108412822B (en) 2017-11-30 2017-11-30 Position compensation telescopic boarding trestle rotation hydraulic system and working method

Country Status (1)

Country Link
CN (1) CN108412822B (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109505810B (en) * 2018-12-29 2023-07-28 大连华锐重工集团股份有限公司 Special driving hydraulic system for multifunctional automatic compensation gangway ladder and control method thereof
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
CN116044843B (en) * 2023-02-01 2023-07-07 北京千尧新能源科技开发有限公司 Floating type hydraulic control system for boarding bridge

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN203939791U (en) * 2013-10-22 2014-11-12 陕西盛迈石油有限公司 Hydraulic slewing system
CN206290504U (en) * 2016-12-21 2017-06-30 四川理工学院 A kind of large-scale steel grasping machine hydraulic gyration energy conserving system

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL271083A (en) * 1960-11-07 1900-01-01
US9938691B2 (en) * 2013-01-08 2018-04-10 Hitachi Construction Machinery Co., Ltd. Hydraulic system for work machine
CN203547527U (en) * 2013-10-23 2014-04-16 福田雷沃国际重工股份有限公司 Rotary drilling rig-controlled rotation hydraulic loop system
JP6190728B2 (en) * 2014-01-24 2017-08-30 Ｋｙｂ株式会社 Hybrid construction machine control system
CN106402059A (en) * 2016-12-26 2017-02-15 徐工集团工程机械有限公司 Load port individual valve, hydraulic bus control system and engineering machinery

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN203939791U (en) * 2013-10-22 2014-11-12 陕西盛迈石油有限公司 Hydraulic slewing system
CN206290504U (en) * 2016-12-21 2017-06-30 四川理工学院 A kind of large-scale steel grasping machine hydraulic gyration energy conserving system

Also Published As

Publication number Publication date
CN108412822A (en) 2018-08-17

Similar Documents

Publication Publication Date Title
CN108438150B (en) Working method of position compensation telescopic boarding trestle
CN108411766B (en) Position compensation telescopic boarding trestle control system and control method
CN108425315B (en) Position compensation retractable landing stage
CN108412822B (en) Position compensation telescopic boarding trestle rotation hydraulic system and working method
CN108105187B (en) A kind of position compensation extension type is gone on board trestle hydraulic system
CN105923110B (en) A kind of compensation of undulation intelligently steps on quadrupler
US4366591A (en) Automatic safety gangplank
CN102173367B (en) Stern hydraulic rudder installing walking trolley
CN109466718B (en) Lifting ship balance system and working method thereof
CN202143760U (en) Hydraulic power and hinge connecting rod type rapid lifting aerial ladder truck
CN105329412B (en) Articulated type extension ladder peculiar to vessel
CN107539888A (en) Fluid pressure type low pressure shore connection cable lifting conveying long-distance monitorng device and its method of work
US20080230321A1 (en) Portable freestanding elevator
CN109178223A (en) A kind of multi-functional automatic compensation gangway ladder
CN109737110B (en) Small-size step bridge based on hydraulic system
CN109707681B (en) Small-size step bridge owner follow-up hydraulic system
CN106144424A (en) A kind of hydraulic telescopic type conveying arm
CN100472075C (en) Boarding bridge ferry plate hydraulic system
CN113979333B (en) Shipborne self-balancing water crane for rescue of large-scale water plane and method
CN110081034B (en) Small-size step bridge hydraulic system
CN108425898B (en) Position compensation telescopic boarding trestle variable-amplitude hydraulic system and working method
CN207700033U (en) A kind of position compensation extension type is gone on board trestle
RU2585181C1 (en) Launching and lifting device
CN208963273U (en) A kind of multi-functional automatic compensation gangway ladder
CN106986274A (en) A kind of container crane and its method of work

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant