CN109707681A - A kind of main follow-up hydraulic system of small-sized fore-and-aft gangway - Google Patents
A kind of main follow-up hydraulic system of small-sized fore-and-aft gangway Download PDFInfo
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- CN109707681A CN109707681A CN201811307435.5A CN201811307435A CN109707681A CN 109707681 A CN109707681 A CN 109707681A CN 201811307435 A CN201811307435 A CN 201811307435A CN 109707681 A CN109707681 A CN 109707681A
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Abstract
The invention discloses the main follow-up hydraulic systems of small-sized fore-and-aft gangway, including main oil supply system and rotary system；Main oil supply system includes fuel tank, the first hydraulic pump being connected on fuel tank and the second hydraulic pump；First hydraulic pump is driven by motor M1, and the second hydraulic pump is driven by motor M2；The output end of first hydraulic pump and the second hydraulic pump collects to form total output end；Rotary system includes revolution electric proportional valve, and revolution electric proportional valve has rotary motor by the first pipeline of revolution and the second piping connection of revolution；Revolution balanced valve is connected with turning round between the second pipeline of the first pipeline and revolution；By in rotary motor braking mechanism piping connection to rotary motor braking mechanism on revolution balanced valve.Using system of the invention, servo-actuated to the master of rotary system can accurately be switched.
Description
Technical field
This invention She is Ji Walk bridge, the especially small-sized main follow-up hydraulic system of fore-and-aft gangway.
Background technique
Walk bridge or trestle are mainly used to conveying personnel or cargo, and in land, the construction of , Walk bridge is relatively easy, but use exists
Marine builds with regard to relative difficult for conveying personnel and goods and materials Walk bridge between two ships, because, between ship and ship
It mutually moves, is generally built on a ship because of Ci , Walk bridge, if necessary to use, by overlapped mode in two ships
Between She Zhi Walk bridge.And during the lapping process, to realize better overlap joint, it is necessary to the phase between Kao Lv Walk bridge and another ship
To position, otherwise can because of ship floating and make into Walk bridge and foul；After the completion of overlap joint, also need to consider between two ships
Relative position, allow Walk bridge to be in the state that passively compensates according to the relative position of two ships, in this way, just can guarantee normally makes
With；In addition, be in an emergency Xia , Walk bridge and another ship to be able to achieve ejection escape, to guarantee security performance.
A kind of fore-and-aft gangway device, including base are disclosed in the patent document that Chinese Patent Application No. is 201510045917.8
Seat and the revolving platform being mounted on above the pedestal, the revolving platform are connected by swing mechanism with the pedestal, institute
It states and is provided with driver's cabin on revolving platform, the revolving platform is connected with fore-and-aft gangway, and the two sides of the fore-and-aft gangway have safety barrier,
The suspension end of the fore-and-aft gangway is provided with docking facilities.The present invention is compared to the prior art, and reasonable structural arrangement, operation are flat
Surely, conveying people between ship and ocean platform can be being realized under complicated, adverse circumstances.Shang Shu Walk Biodge device, although can be real
Personnel and Material Transportation between spot oceangoing ship, but Da Jie Walk Biodge device and Da Jie Walk Biodge device Hou , Walk Biodge device cannot root
The problems such as carrying out corresponding change in location according to the change in location between ship, be easy to appear accident, and in emergency circumstances , Walk
Bridge can not carry out ejection escape.
A kind of full hydraulic drive is disclosed in the patent document that Chinese Patent Application No. is 200610049538.7 to go on board
Ladder, by be fixed on the main ladder that constitutes on harbour with the ladder for running ladder with can activity on the face of boat deck with triangle ladder, gangway ladder
Auxiliary ladder composition, the auxiliary ladder by connected on slide and slide luffing, rotating mechanism, hydraulic station, pulley device and be fixed on code
Hoisting mechanism on head is constituted, and lift cylinder goes up and down the pulley device on slide along the I-steel guide rail on ladder, slide
On rotating platform in the horizontal plane around center axis rotation, the hinged gangway ladder in rotating platform front end, flexible by amplitude oil cylinder makes
Support of the gangway ladder on rotating platform rotates on the vertical plane, and the height of adjusting triangle ladder, gangway ladder, rotary oil cylinder makes gangway ladder in water
It is rotated within the scope of 120 degree of plane, hydraulic station, luffing, rotating mechanism are gone up and down in slide and with slide, compact-sized, simplified
Oil circuit reduces oil pipe, and use is safe and reliable, and the stability of synchronization is good for work, high sensitivity, particularly suitable in oil product, chemical industry code
Meets the needs of drop changes greatly on head.Although above structure produces certain benefit, but ship is operation or rests in
Waterborne, due to the influence of factors, ship can generate heave, shaking etc., therefore bring very big trouble to overlap joint, and
And after overlapping, if auxiliary ladder can not achieve servo-actuated, it is easily damaged boarding ladder, can not carry out smoothly remarkable and transports object
Money.
A kind of Three Degree Of Freedom wave benefit is disclosed in the patent document that Chinese Patent Application No. is 201611205250.4
Repay to step on and multiply trestle, technical solution is: it includes: base platform, control system, attitude transducer, trestle support, and trestle is logical
Road, amplitude oil cylinder, rolling compensating cylinder；Ship rolling, pitching, heave movement are mended in real time although the present invention can be realized
It repays, but changes not record in technical solution be how to control amplitude oil cylinder, rolling compensating cylinder, which is accomplished that
Active Compensation, after trestle channel has overlapped, it is necessary to it is controlled by control system, and when control system needs certain reaction
Between, therefore, the phenomenon that being easy to appear delays time to control, while it is also big to consume energy, and the heavier-weight in trestle channel, when trestle channel
After putting up, the weight in trestle channel is largely fallen in overlapped points.
A kind of marine transportation and sea are disclosed in the patent document that Chinese Patent Application No. is 201610396070.2
It being stepped on compensation of undulation function by device and method in shipping work field, stepping on forward, gangway ladder is perpendicular to deck and fixed connects
Gangway ladder bracket is connect, motion controller first controls active compensation of undulation platform to the rolling of ship, pitching and heave real-time compensation, then
Motor reversal is controlled, motor drives wirerope to discharge gangway ladder, and gangway ladder rotates counterclockwise around universal joint, when gangway ladder angular transducer is examined
Measure gangway ladder with respect to upper mounting plate release rotate to predetermined angle when, motor shuts down；It steps on after leaning on, motion controller control
Motor rotates forward, when gangway ladder angular transducer detects that gangway ladder rotates to predetermined angle with respect to upper mounting plate, gangway ladder perpendicular to deck,
Gangway ladder is fixed on gangway ladder bracket；The rolling, pitching and heave of compensation of undulation platform real-time compensation ship in severe sea situation,
Automatic deploying and retracting gangway ladder just carries out folding and unfolding when compensating for upper mounting plate to certain steady state, improve step on by when stationarity and peace
Quan Xing.The structure is that the position of platform is adjusted by active compensation of undulation, then realizes overlap joint, and since ship is to shake,
It is difficult to ensure the position between gangway ladder and ship during the lapping process, overlap joint is very difficult, after overlap joint, if gangway ladder cannot be real
It is now servo-actuated, is then easily damaged the structure, can not carry out smoothly remarkable and transport goods and materials.
For little Xing Walk bridge, weight is relatively light very much, and it is convenient to use, and during the lapping process, generallys use
Fast junction apparatus is docked, but in actual application, due to the rolling of hull, Mu Qian Walk bridge can be carried out
Better rolling compensation.In addition, the reason of because of control system and hydraulic system, the job insecurity of Zao Cheng Walk bridge.
Summary of the invention
It, can be to returning using system of the invention the object of the present invention is to provide a kind of small-sized main follow-up hydraulic system of fore-and-aft gangway
The master for transfering from one department to another system, which is servo-actuated, accurately to be switched.
In order to achieve the above objectives, a kind of main follow-up hydraulic system of small-sized fore-and-aft gangway, including main oil supply system and rotary system；
Rotary system includes revolution electric proportional valve, and revolution electric proportional valve is connected by the first pipeline of revolution and the second pipeline of revolution
It is connected to rotary motor；Revolution balanced valve is connected with turning round between the second pipeline of the first pipeline and revolution；On revolution balanced valve
By in rotary motor braking mechanism piping connection to rotary motor braking mechanism；
Revolution shuttle valve is equipped on rotary motor braking mechanism pipeline, the wherein input terminal connection revolution for turning round shuttle valve is flat
Weigh valve, turns round the output end connection revolution motor brake mechanism of shuttle valve；
The main servo-actuated solenoid directional control valve of revolution, the end P of main servo-actuated solenoid directional control valve are connected in revolution another input terminal of shuttle valve
Total output end is connected, the end T of main servo-actuated solenoid directional control valve is connected on oil return line L, the end the B connection of main servo-actuated solenoid directional control valve
Onto revolution shuttle valve；
First is connected between the second pipeline of the first pipeline of revolution between revolution balanced valve and rotary motor and revolution
Servo-actuated shuttle valve, the output end of the first servo-actuated shuttle valve are connected with the first servo-actuated overflow valve, the output end connection of the first servo-actuated overflow valve
To fuel tank, be parallel with the second servo-actuated shuttle valve on the first servo-actuated shuttle valve, the output end of the second servo-actuated shuttle valve connects fuel tank, first with
X mouth of dynamic overflow valve is connected with servo-actuated two logical pilot operated directional control valves, be servo-actuated two logical pilot operated directional control valves be connected with second with
The output end of dynamic overflow valve, the second servo-actuated overflow valve connects oil return line L, is servo-actuated a wherein control of two logical pilot operated directional control valves
End processed connects oil return line L, and another control terminal of servo-actuated two logical pilot operated directional control valves is connected to the B of main servo-actuated solenoid directional control valve
End.
Above-mentioned rotary system, when the first hydraulic pump and the second hydraulic pump works, hydraulic oil enters back from total output end
Turn electric proportional reversing valve；Electric proportional reversing valve is turned round in control, and hydraulic oil is turned round electric proportional reversing valve and entered in angling cylinder,
Promoting turning oil cylinder rotation.The positive and negative rotation of angling cylinder turns round the position of electric proportional reversing valve by control to realize.Revolution oil
Cylinder work while, hydraulic oil from revolution shuttle valve enter in rotary motor braking mechanism, to rotary motor braking mechanism into
Row brake releases.
It if necessary to turn round servo-actuated compensation, gives revolution main servo-actuated electromagnetic switch valve control signal, turns round main servo-actuated electromagnetism and change
It replaces to valve, hydraulic oil controls from the servo-actuated solenoid directional control valve of revolution master and is servo-actuated two logical pilot operated directional control valves, is servo-actuated two one and leads to
Pilot operated directional control valve transposition, the X mouth of the first servo-actuated overflow valve is connected to the second servo-actuated overflow valve, due to the pressure of the first servo-actuated overflow valve
Power is greater than the pressure of the second servo-actuated overflow valve, therefore, when the hydraulic fluid pressure in rotary motor is greater than the second servo-actuated overflow valve
When pressure, the first servo-actuated overflow valve is connected, the hydraulic oil in rotary motor can both ends by the first servo-actuated shuttle valve and second with
Dynamic shuttle valve flows freely, and plays the role of the servo-actuated compensation of revolution.In this way, being able to achieve main servo-actuated accurate switching.
Further, main accumulator combination valve is connected on total output end；Main accumulator combination valve includes accumulator two
Position two-way pilot operated directional control valve, accumulator two-position two-way electromagnetic directional valve, accumulator overflow valve；Total output end is connected with accumulator,
Total output end is connect with the input terminal of accumulator overflow valve, and the output end of accumulator overflow valve connects fuel tank；Total output end connection
To the end accumulator two-position two-way hydraulic control reversal valve P, the end the A connection rolling compensation system of accumulator two-position two-way hydraulic control reversal valve,
Pitch compensation system, telescopic system and rotary system；A wherein control terminal for accumulator two-position two-way hydraulic control reversal valve, which connects, to be stored
The end A and the end P of energy device two-position two-way hydraulic control reversal valve, another control terminal of accumulator two-position two-way hydraulic control reversal valve connect accumulator
Another control terminal at the end A and the end P of two-position two-way hydraulic control reversal valve, accumulator two-position two-way hydraulic control reversal valve connects accumulator two
Two electric change valves of position, accumulator two-position two-way electromagnetic directional valve connect oil return line L.
When the first hydraulic pump and the second hydraulic pump works, hydraulic oil can be stand-by directly to main accumulator accumulation of energy, if main storage
The pressure of energy device is excessive, then accumulator overflow valve overflow.When there is hydraulic oil to enter accumulator two-position two-way hydraulic control reversal valve P
End, the transposition of accumulator two-position two-way hydraulic control reversal valve, the end P of accumulator two-position two-way hydraulic control reversal valve are connected to the end A, realization pair
Rolling compensation system, pitch compensation system, telescopic system and rotary system fuel feeding.
Further, it is equipped with revolution pressure valve between total output end and the electric proportional reversing valve of revolution, turns round the X mouth of pressure reducing valve
Be connected with the second shuttle valve, two input terminals of the second shuttle valve respectively with the first pipeline of revolution and turn round the second piping connection.Pass through
Two shuttle valves and acting on for revolution pressure reducing valve allow the pressure of output to be stablized to control the output pressure of revolution pressure reducing valve.
Detailed description of the invention
Fig. 1 is main oil way of hydraulic system partial schematic diagram.Fig. 2 is hydraulic system execution part system.E's puts in Fig. 3 Fig. 1
Big figure.Fig. 4 is the enlarged drawing of F in Fig. 1.Fig. 5 is the enlarged drawing of G in Fig. 2.Fig. 6 is the enlarged drawing of H in Fig. 2.Fig. 7 is I in Fig. 2
Enlarged drawing.Fig. 8 is the partial schematic diagram of rotary system.
Specific embodiment
The present invention will be described in further detail with reference to the accompanying drawings and detailed description.
As depicted in figs. 1 and 2, little Xing Walk bridge hydraulic system includes main oil supply system 1a, permanent thrust accumulator system 2a, cross
Shake compensation system 3a, pitch compensation system 4a, telescopic system 5a and rotary system 6a.
Wherein main oil supply system and rotary system constitute the main follow-up hydraulic system of little Xing Walk bridge of the invention.
Main oil supply system 1a includes fuel tank 11a, the first hydraulic pump 12a being connected on fuel tank 11a and the second hydraulic pump
13a；First hydraulic pump 12a is driven by motor M1, and the second hydraulic pump 13a is driven by motor M2；First hydraulic pump 12a and
The output end of two hydraulic pump 13a collects to form total output end O.
After motor M1 and motor M2 start, the first hydraulic pump 12a and the second hydraulic pump 13a starting, by hydraulic oil from oil
Case 11a is pumped out to total output end O.Using multiple hydraulic pumps, the oil pressure and flow in hydraulic system can be improved, while ought wherein one
Hydraulic pump damage, hydraulic pump in addition can play the role of emergency.
As shown in figures 1 and 3, main accumulator combination valve 7a is connected on total output end O；Main accumulator combination valve 7a packet
Include accumulator two-position two-way hydraulic control reversal valve 71a, accumulator two-position two-way electromagnetic directional valve 72a, accumulator overflow valve 73a；Always
Output end O is connected with accumulator 74a, and total output end O is connect with the input terminal of accumulator overflow valve 73a, accumulator overflow valve 73a
Output end connect fuel tank 11a；Total output end O is connected to the end P of accumulator two-position two-way hydraulic control reversal valve 71a, accumulator two
The end A connection rolling compensation system, pitch compensation system, telescopic system and the rotary system of position two-way pilot operated directional control valve 71a；Accumulation of energy
The end A of the wherein control terminal connection accumulator two-position two-way hydraulic control reversal valve 71a of device two-position two-way hydraulic control reversal valve 71a and P
End, the end A of another control terminal connection accumulator two-position two-way hydraulic control reversal valve 71a of accumulator two-position two-way hydraulic control reversal valve 71a
Accumulator two-position two-way electromagnetic directional valve 72a is connected with another control terminal at the end P, accumulator two-position two-way hydraulic control reversal valve 71a,
Accumulator two-position two-way electromagnetic directional valve 72a connection oil return line L；Total output end O is connected to permanent thrust by oil charge valve 20a and stores
It can device system 2a.
When the first hydraulic pump 12a and the second hydraulic pump 13a works, hydraulic oil can be stand-by directly to main accumulator accumulation of energy, such as
The pressure of the main accumulator of fruit is excessive, then accumulator overflow valve 73a overflow.When there is hydraulic oil to enter accumulator two-position two-way hydraulic control
The end reversal valve 71aP, accumulator two-position two-way hydraulic control reversal valve 71a transposition, the end P of accumulator two-position two-way hydraulic control reversal valve 71a
It is connected to, is realized to rolling compensation system, pitch compensation system, telescopic system and rotary system fuel feeding with the end A.If oil charge valve changes
Position, then can be oil-filled to permanent thrust accumulator system.
Permanent thrust accumulator system 2a is connected to total output end O, and permanent thrust accumulator system 2a has output end PP；Perseverance pushes away
Power accumulator system 2a is used to provide permanent thrust to telescopic oil cylinder, allows telescopic oil cylinder to move in servomechanism process more steady,
To make the movement of Telescopic path steady.
As shown in Figure 1 and Figure 4, permanent thrust accumulator system 2a include oil-filled pressure reducing valve 21a, it is oil-filled check valve 22a, oil-filled
Hand-operated valve 23a, the hand-operated valve 24a that drains the oil, oil-filled overflow valve 25a and permanent thrust accumulator 26a；It is oil-filled pressure reducing valve 21a, oil-filled unidirectional
Valve 22a, oil-filled hand-operated valve 23a and perseverance thrust accumulator 26a are sequentially connected, and oil-filled pressure reducing valve 21a is connected to total output end O, puts
The other end that one end of oily hand-operated valve 24a connects permanent thrust accumulator 26a, the hand-operated valve 24a that drains the oil connects fuel tank 11a, oil-filled to overflow
The input terminal for flowing valve 25a connects the output end connection fuel tank 11a of permanent thrust accumulator 26a, oil-filled overflow valve 25a；Permanent thrust stores
The output end of energy device 26a is PPEnd.
Above-mentioned oil-filled process are as follows: open oil-filled hand-operated valve 23a, hydraulic oil is through oil charge valve, oil-filled pressure reducing valve 21a, oil-filled
Check valve 22a, oil-filled hand-operated valve 23a enter permanent thrust accumulator 26a, and such as permanent thrust accumulator 26a then passes through oil-filled overflow
Valve 25a overflow.If discharging the hydraulic oil of permanent thrust accumulator 26a, the hand-operated valve 24a that drains the oil is opened.
As shown in Fig. 2, rolling compensation system 3a includes rolling electricity proportional reversing valve 31a and rolling combination valve block 32a, rolling
Electric proportional reversing valve 31a is connect with total output end O, and rolling electricity proportional reversing valve 31a passes through rolling the first pipeline 34a and rolling the
Two pipeline 35a are connected with rolling oil cylinder 3, and rolling combination valve block 32a is connected to the second pipeline of rolling the first pipeline 34a and rolling
Between 35a.
As shown in figure 4, rolling combination valve block 32a includes the first balanced valve of rolling 321a, the second balanced valve of rolling 322a, cross
Shake the first shuttle valve 323a, the second shuttle valve of rolling 324a, the first check valve of rolling 325a, rolling second one-way valve 326a, rolling
One overflow valve 327a and the second overflow valve of rolling 328a；The first balanced valve of rolling 321a is connected on the first pipeline of rolling 34a, horizontal
The second balanced valve 322a is shaken to be connected on the second pipeline of rolling 35a；An input terminal of the first shuttle valve of rolling 323a is connected to rolling
The input terminal of first balanced valve 321a, another input terminal of the first shuttle valve of rolling 323a are connected to the one of the second shuttle valve of rolling 324a
Another input terminal of input terminal, the second shuttle valve of rolling 324a is connected to the input terminal of the second balanced valve of rolling 322a；Rolling first
The output end of shuttle valve 323a is connected on the second balanced valve of rolling 322a, and the output end of the second shuttle valve of rolling 324a is connected to rolling
On first balanced valve 321a；The output end of the first check valve of rolling 325a is connected to the output end of the first balanced valve of rolling 321a,
The output end of rolling second one-way valve 326a is connected to the output end of the second balanced valve of rolling 322a, the first check valve of rolling 325a
Fuel tank 11a is connected to the input terminal of rolling second one-way valve 326a, the input terminal of the first overflow valve of rolling 327a, which is connected to, to be located at
Between rolling the first balanced valve 321a output end and rolling oil cylinder 3, the output end of the first overflow valve of rolling 327a connects fuel tank
11a, the input terminal of the second overflow valve of rolling 328a be connected to positioned at rolling the second balanced valve 322a output end and rolling oil cylinder 3 it
Between, the output end of the second overflow valve of rolling 328a connects fuel tank 11a；In rolling the first shuttle valve 323a and the second shuttle valve of rolling 324a
Between be connected with rolling two-position four-way solenoid valve, the end P of rolling two-position four-way solenoid valve is connect with total output end O, rolling two
The end T of four way solenoid valve is connect with the end fuel tank 11a, and the end B of rolling two-position four-way solenoid valve is connected to the first shuttle valve of rolling 323a
Between the second shuttle valve of rolling 324a.
Above-mentioned rolling replenishment system, when the first hydraulic pump 12a and the second hydraulic pump 13a works, hydraulic oil is exported from total
End O enters rolling electricity proportional reversing valve 31a；Rolling electricity proportional reversing valve 31a is controlled, hydraulic oil is through rolling electricity proportional reversing valve
31a is entered in rolling oil cylinder 3 by rolling combination valve block 32a, and rolling oil cylinder 3 is pushed to move.
In normal work, enter such as hydraulic oil from rolling the first pipeline 34a, hydraulic oil passes through the first balanced valve of rolling
321a is entered in rolling oil cylinder 3, and the hydraulic oil in rolling oil cylinder 3 is from rolling the second pipeline 35a through the second balanced valve of rolling
322a returns to fuel tank 11a from rolling electricity proportional reversing valve 31a, meanwhile, the part liquid of the input terminal of the first balanced valve of rolling 321a
Pressure oil enters rolling the second balanced valve 322a from the first shuttle valve of rolling 323a, controls the flow of the second balanced valve of rolling 322a,
Play the role of balancing rolling the first pipeline 34a and rolling the second pipeline 35a hydraulic fluid pressure and flow, while rolling second is flat
Weighing apparatus valve 322a can improve back pressure, avoid the quick emptying of rolling oil cylinder 3 and cause rolling velocity too fast.As the first pipeline of rolling 34a
Hydraulic fluid pressure be greater than the pressure of the first overflow valve of rolling 327a, then there is overflow phenomena, guarantee enters in rolling oil cylinder 3
Oil pressure stablize.
If hydraulic oil enters from rolling the second pipeline 35a, hydraulic oil enters rolling by the second balanced valve of rolling 322a
In oil cylinder 3, hydraulic oil in rolling oil cylinder 3 is from rolling the first pipeline 34a through rolling the first balanced valve 321a from rolling electricity ratio
Reversal valve 31a returns to fuel tank 11a, meanwhile, the section hydraulic oil of the input terminal of the second balanced valve of rolling 322a is from the second shuttle of rolling
Valve 324a enters rolling the first balanced valve 321a, controls the flow of the first balanced valve of rolling 321a, plays balance rolling first
The effect of pipeline 34a and rolling the second pipeline 35a hydraulic fluid pressure and flow, while the first balanced valve of rolling 321a can improve back
Pressure, avoids the quick emptying of rolling oil cylinder 3 and causes rolling velocity too fast.When the hydraulic fluid pressure of the second pipeline of rolling 35a is greater than
Then there is overflow phenomena in the pressure of the second overflow valve of rolling 328a, guarantees that the oil pressure entered in rolling oil cylinder 3 is stablized.
Such as rolling is needed to compensate, allow rolling two-position four-way solenoid valve replace, hydraulic oil through rolling two-position four-way solenoid valve into
Enter between rolling the first shuttle valve 323a and the second shuttle valve of rolling 324a, then balances rolling first under the action of hydraulic oil
Valve 321a and the 322a short circuit of the second balanced valve of rolling, hydraulic oil can be directly over rolling the first balanced valve 321a or rolling second is flat
Weighing apparatus valve 322a, rolling the first balanced valve 321a and the second balanced valve of rolling 322a will not provide any pressure, in this way, being able to achieve
Fast, accurately rolling compensates, the speeds match of the speed and rolling that allow rolling to compensate, the work smoothness of Ti Gao Walk bridge.
As shown in Fig. 2, pitch compensation system 4a includes pitching electricity proportional reversing valve 41a and pitching combination valve block 42a, pitching
Electric proportional reversing valve 41a is connect with total output end O, and pitching electricity proportional reversing valve 41a is bowed by the first pitch conduit 44a and second
Face upward pipeline 45a and be connected with amplitude oil cylinder, pitching combination valve block 42a be connected to the first pipeline of pitching and the second pipeline of pitching it
Between；
As shown in fig. 6, pitching combination valve block 42a includes pitching balanced valve 421a, the first shuttle valve of pitching 422a, pitching second
Shuttle valve 423a, the first check valve of pitching 424a, pitching second one-way valve 425a, pitching the first overflow valve 426a and pitching second are overflow
Flow valve 427a；Pitching balanced valve 421a is connected on the second pipeline of pitching；An input terminal of the first shuttle valve of pitching 422a is connected to
On the first pipeline of pitching 44a, the output end of the first shuttle valve of pitching 422a is connected to an input terminal of the second shuttle valve of pitching 423a, bows
Another input terminal for facing upward the second shuttle valve 423a is connected to the input terminal of pitching balanced valve 421a；The output of the second shuttle valve of pitching 423a
End is connected on pitching balanced valve 421a；The output end of the first check valve of pitching 424a is connected on the first pipeline of pitching 44a, is bowed
The output end for facing upward second one-way valve 425a is connected to the output end of pitching balanced valve, pitching the first check valve 424a and pitching second
The input terminal of check valve 425a is connected to fuel tank 11a, and the input terminal of the first overflow valve of pitching 426a is connected to the first pipeline of pitching 44a
On, the output end of the first overflow valve of pitching 426a connects fuel tank 11a, and the input terminal of the second overflow valve of pitching 427a, which is connected to, to be located at
Between pitching balanced valve output end and amplitude oil cylinder 9, the output end of the second overflow valve of pitching 427a connects fuel tank 11a；In pitching
Another input terminal of first shuttle valve 422a is connected with pitching two-position four-way solenoid valve 428a, pitching two-position four-way solenoid valve 428a's
The end P is connect with total output end O, and the end T of pitching two-position four-way solenoid valve 428a is connect with the end fuel tank 11a, pitching two-position four-way electricity
The end B of magnet valve 428a is connected to another input terminal of the first shuttle valve of pitching 422a.
It is connected with the main servo-actuated solenoid directional control valve 429a of pitching in total output end O, wherein the main servo-actuated solenoid directional control valve of pitching
The end P of 429a connects total input terminal, and the end T of the main servo-actuated solenoid directional control valve 429a of pitching connects fuel tank 11a, the main servo-actuated electromagnetism of pitching
The end B of reversal valve 429a is connected on the second pipeline of pitching.
Hydraulic control one-way valve, the control of hydraulic control one-way valve are connected separately on the second pipeline of pitching the first pipeline 44a and pitching
End processed is connect with the end B of the main servo-actuated solenoid directional control valve 429a of pitching.
Above-mentioned pitching replenishment system, when the first hydraulic pump 12a and the second hydraulic pump 13a works, hydraulic oil is exported from total
End O enters pitching electricity proportional reversing valve 41a；Pitching electricity proportional reversing valve 41a is controlled, hydraulic oil is through pitching electricity proportional reversing valve
41a is entered in amplitude oil cylinder by pitching combination valve block 42a, pushes amplitude oil cylinder movement.
In normal work, the main servo-actuated solenoid directional control valve 429a of pitching does not give signal, if hydraulic oil is from the first pipeline of pitching
44a enters, and hydraulic oil enters in amplitude oil cylinder by pitching balanced valve 421a, and the hydraulic oil in amplitude oil cylinder is from pitching second
Pipeline returns to fuel tank 11a from pitching electricity proportional reversing valve 41a.When the hydraulic fluid pressure of the first pipeline of pitching 44a is greater than pitching the
, then there is overflow phenomena in the pressure of one overflow valve 426a, and guarantee enters the in-oil cylinder oil pressure of pitching and stablizes.
If hydraulic oil enters from the second pipeline of pitching, hydraulic oil enters in amplitude oil cylinder by the second pipeline of pitching, horizontal
Hydraulic oil in amplitude oil cylinder returns to fuel tank 11a from luffing electricity proportional reversing valve through luffing balanced valve from the first pipeline of luffing, together
When, it is flat that section hydraulic oil on the second pipeline of pitching from pitching the first shuttle valve 422a and the second shuttle valve of pitching 423a enters pitching
Weigh valve 421a, controls the flow of pitching balanced valve 421a, plays balance pitching the first pipeline 44a and pitching the second hydraulic pressure of pipe line oil
The effect of pressure and flow, while pitching balanced valve 421a can improve back pressure, avoid the quick emptying of amplitude oil cylinder and cause luffing
Excessive velocities.When pressure of the hydraulic fluid pressure of the second pipeline of pitching greater than the second overflow valve of pitching 427a, then it is existing to there is overflow
As guaranteeing that the oil pressure entered in amplitude oil cylinder is stablized.
Active pitch compensation is such as needed, allows pitching two-position four-way solenoid valve 428a to replace, hydraulic oil is through pitching two-position four-way
Solenoid valve 428a enters pitching the first shuttle valve 422a, then enters the second shuttle valve of pitching from the first shuttle valve of pitching 422a
423a, hydraulic oil enter pitching balanced valve 421a from the second shuttle valve of pitching 423a, balance pitching under the action of hydraulic oil
Valve 421a short circuit, hydraulic oil can be directly over pitching balanced valve 421a, and pitching balanced valve 421a will not provide any pressure, this
Sample is able to achieve fast, accurately pitch compensation, allows the speed of horizontal pitch compensation and the speeds match of pitching, the work of Ti Gao Walk bridge
Make stationarity.
After docking facilities are to connecting, servo-actuated pitch compensation is carried out, principle is: the main servo-actuated solenoid directional control valve of pitching
429a is powered, and the main servo-actuated solenoid directional control valve 429a of pitching is allowed to replace, and allows it to replace to pitching two-position four-way solenoid valve 428a energization,
Hydraulic oil enters pitching the first shuttle valve 422a through pitching two-position four-way solenoid valve 428a, then from pitching the first shuttle valve 422a into
Enter to pitching the second shuttle valve 423a, hydraulic oil enters pitching balanced valve 421a from the second shuttle valve of pitching 423a, in hydraulic oil
By the 421a short circuit of pitching balanced valve under effect, hydraulic oil can be directly over pitching balanced valve 421a, and pitching balanced valve 421a will not
Any pressure is provided, meanwhile, hydraulic oil enters the control terminal of hydraulic control one-way valve through the main servo-actuated solenoid directional control valve 429a of pitching,
Hydraulic oil in amplitude oil cylinder returns to fuel tank 11a from hydraulic control one-way valve, servo-actuated compensation is realized, since pitching balanced valve 421a is short
Road, therefore, the work for being able to achieve quick, precision compensation , Rang Walk bridge are more steady.
The work that the pitch compensation system is able to achieve active, Active Compensation and servo-actuated compensation , Rang Walk bridge is more flat
Surely.
As shown in Fig. 2, telescopic system 5a includes flexible electricity proportional reversing valve 51a and flexible combination valve 52a, electricity ratio of stretching
Reversal valve 51a is connect with total output end O, and the electricity proportional reversing valve 51a that stretches is connected by flexible first pipeline and flexible second pipeline
It is connected to telescopic oil cylinder, flexible combination valve 52a is connected on flexible first pipeline 54a and flexible second pipeline 55a.
As shown in fig. 7, flexible combination valve 52a group includes flexible balanced valve 521a, two logical one 522a of pilot operated directional control valve
Flexible first pipeline 54a and flexible second pipeline are connected to two logical two 523a of pilot operated directional control valve, flexible balanced valve 521a
Between 55a, the end A of two logical one 522a of pilot operated directional control valve connects PpThe end B at end, two logical one 522a of pilot operated directional control valve connects
The end A of two logical two 523a of pilot operated directional control valve is connect, the end B of two logical two 523a of pilot operated directional control valve is connected to flexible second pipe
On the 55a of road, the end B of two logical one 522a of pilot operated directional control valve is connected on flexible first pipeline 54a；Two logical liquid controlled reversings
One end control terminal of one 522a and two logical two 523a of pilot operated directional control valve of valve is connected on oil return line L after converging, and two one
The other end control terminal of logical one 522a and two logical two 523a of pilot operated directional control valve of pilot operated directional control valve is connected with flexible master after converging
On servo-actuated solenoid directional control valve 524a, the end P for the main servo-actuated solenoid directional control valve 524a that stretches connects PpEnd, stretch main servo-actuated electromagnetic switch
The end T of valve 524a connects fuel tank 11a, the end B for the main servo-actuated solenoid directional control valve 524a that stretches and two logical pilot operated directional control valves one
The other end control terminal point connection of 522a and two logical two 523a of pilot operated directional control valve.
Above-mentioned telescopic system, when the first hydraulic pump 12a and the second hydraulic pump 13a work, hydraulic oil from total output end O into
Enter to flexible electric proportional reversing valve 51a；The flexible electric proportional reversing valve 51a of control, hydraulic oil are logical through flexible electricity proportional reversing valve 51a
It crosses flexible combination valve 52a group to enter in telescopic oil cylinder, pushes telescopic oil cylinder movement.
In normal work, signal is not controlled to flexible main servo-actuated solenoid directional control valve 524a, if hydraulic oil is from flexible first
Pipeline 54a is entered in telescopic oil cylinder, and the hydraulic oil in telescopic oil cylinder is from flexible second pipeline 55a from flexible electric proportional reversing valve
51a returns to fuel tank 11a.Due to being provided with flexible balanced valve 521a, it is adjustable flexible first pipeline 54a and flexible second
The pressure and flow of pipeline 55a.
It after docking facilities are to connecting, needs to carry out follow-up telescoping compensation, principle is: flexible electricity proportional reversing valve 51a
It resets, controls signal to the flexible main solenoid directional control valve 524a that is servo-actuated, allow flexible main servo-actuated solenoid directional control valve 524a to replace, PpEnd
Hydraulic oil is servo-actuated solenoid directional control valve 524a two one 522a and two logical hydraulic controls of logical pilot operated directional control valve of control from flexible master and changes
To two 523a of valve, two logical pilot operated directional control valves, one 522a and two logical two 523a of pilot operated directional control valve transposition, PpThat holds is hydraulic
Oil gives one constant thrust of telescopic oil cylinder, allows telescopic oil cylinder at the uniform velocity to compensate, in this process, if the pressure of telescopic oil cylinder
It is small, then pressure, if the pressure of telescopic oil cylinder is excessive, the pressure reservoir of telescopic oil cylinder are provided by permanent thrust accumulator system
Into permanent thrust accumulator system, so that expanding-contracting action is steady.
As shown in Fig. 2, rotary system 6a includes revolution electric proportional valve 61a, revolution electric proportional valve 61a passes through the first pipe of revolution
Road 64a and the second pipeline 65a of revolution are connected with rotary motor 61；It is turning round between the second pipeline 65a of the first pipeline 64a and revolution
It is connected with revolution balanced valve 63a；It is stopped on revolution balanced valve 63a by rotary motor braking mechanism piping connection to rotary motor
On mechanism of car 66a.
As shown in figure 8, being equipped with revolution shuttle valve 671a on rotary motor braking mechanism pipeline, revolution shuttle valve 671a is wherein
The output end connection revolution motor brake mechanism 66a of the connection of one input terminal revolution balanced valve 63a, revolution shuttle valve 671a；
It is connected with the main servo-actuated solenoid directional control valve 672a of revolution in revolution another input terminal of shuttle valve 671a, turns round main servo-actuated electromagnetism
The end P of reversal valve connects total output end O, and the end T for turning round main servo-actuated solenoid directional control valve is connected on oil return line L, revolution it is main with
The end B of dynamic solenoid directional control valve is connected on revolution shuttle valve 671a.
Connect between the second pipeline 65a of revolution the first pipeline 64a between revolution balanced valve 63a and rotary motor and revolution
Be connected to the first servo-actuated shuttle valve 673a, the output end of the first servo-actuated shuttle valve 673a is connected with the first servo-actuated overflow valve 675a, first with
The output end of dynamic overflow valve 675a is connected to fuel tank 11a, and the second servo-actuated shuttle valve 674a is parallel on the first servo-actuated shuttle valve 673a,
The output end of second servo-actuated shuttle valve 674a connects fuel tank 11a, and the X mouth of the first servo-actuated overflow valve 675a is connected with servo-actuated two one and leads to
Pilot operated directional control valve 676a, servo-actuated two logical pilot operated directional control valve 676a are connected with the second servo-actuated overflow valve 677a, and second is servo-actuated excessive
The output end for flowing valve 677a connects oil return line L, and a wherein control terminal of servo-actuated two logical pilot operated directional control valve 676a connects back to
Oil pipe line L, another control terminal of servo-actuated two logical pilot operated directional control valve 676a are connected to the end B of main servo-actuated solenoid directional control valve.The
The setting pressure of one servo-actuated overflow valve is greater than the setting pressure of the second servo-actuated overflow valve.
Above-mentioned rotary system, when the first hydraulic pump 12a and the second hydraulic pump 13a work, hydraulic oil from total output end O into
Enter to the electric proportional reversing valve of revolution；Electric proportional reversing valve is turned round in control, and hydraulic oil is turned round electric proportional reversing valve and enters revolution
In oil cylinder, promoting turning oil cylinder rotation.The positive and negative rotation of angling cylinder turns round the position of electric proportional reversing valve by control to realize.
While work, hydraulic oil enters in rotary motor braking mechanism 66a angling cylinder from revolution shuttle valve 671a, to revolution horse
Brake releasing is carried out up to braking mechanism 66a.
If necessary to turn round servo-actuated compensation, signal is controlled to the main servo-actuated solenoid directional control valve 672a of revolution, turns round main servo-actuated electricity
Magnetic reversal valve 672a transposition, hydraulic oil control from the main servo-actuated solenoid directional control valve 672a of revolution and are servo-actuated two logical pilot operated directional control valves
676a is servo-actuated two logical pilot operated directional control valve 676a transpositions, the X mouth and the second servo-actuated overflow valve of the first servo-actuated overflow valve 675a
677a connection, since the pressure of the first servo-actuated overflow valve 675a is greater than the pressure of the second servo-actuated overflow valve 677a, work as revolution
When hydraulic fluid pressure in motor is greater than the pressure of the second servo-actuated overflow valve 677a, the first servo-actuated overflow valve 675a is connected, revolution
Hydraulic oil in motor can be flowed freely at both ends by the first servo-actuated servo-actuated shuttle valve 674a of shuttle valve 673a and second, and revolution is played
The effect of servo-actuated compensation.
As shown in fig. 7, it is equipped with flexible pressure reducing valve between total output end O and flexible electric proportional reversing valve 51a, decompression of stretching
The X mouth of valve is connected with the first shuttle valve, two input terminals of the first shuttle valve respectively with flexible first pipeline 54a and flexible second pipeline
55a connection is respectively equipped with the first overflow valve on flexible first pipeline 54a and flexible second pipeline 55a.By the first shuttle valve with
Acting on for flexible pressure reducing valve allows the pressure of output to be stablized to control the output pressure of flexible pressure reducing valve.
As shown in figure 8, in total output end O and turning round between electric proportional reversing valve equipped with revolution pressure valve, the X of pressure reducing valve is turned round
Mouth is connected with the second shuttle valve, and two input terminals of the second shuttle valve connect with the first pipeline 64a of revolution and the second pipeline 65a of revolution respectively
It connects.The output pressure that revolution pressure reducing valve is controlled by the effect of the second shuttle valve and revolution pressure reducing valve allows the pressure of output to stablize.
Claims (3)
1. a kind of main follow-up hydraulic system of small-sized fore-and-aft gangway, it is characterised in that: including main oil supply system and rotary system；
Main oil supply system includes fuel tank, the first hydraulic pump being connected on fuel tank and the second hydraulic pump；First hydraulic pump passes through electricity
Machine M1 drives, and the second hydraulic pump is driven by motor M2；The output end of first hydraulic pump and the second hydraulic pump collect to be formed it is total defeated
Outlet；
Rotary system includes revolution electric proportional valve, and revolution electric proportional valve has by the first pipeline of revolution and the second piping connection of revolution
Rotary motor；Revolution balanced valve is connected with turning round between the second pipeline of the first pipeline and revolution；Pass through on revolution balanced valve
In rotary motor braking mechanism piping connection to rotary motor braking mechanism；
It is equipped with revolution shuttle valve on rotary motor braking mechanism pipeline, turns round the wherein input terminal connection revolution balance of shuttle valve
Valve turns round the output end connection revolution motor brake mechanism of shuttle valve；
The main servo-actuated solenoid directional control valve of revolution, the end the P connection of main servo-actuated solenoid directional control valve are connected in revolution another input terminal of shuttle valve
The end T of total output end, main servo-actuated solenoid directional control valve is connected on oil return line L, and the end B of main servo-actuated solenoid directional control valve is connected to back
Turn on shuttle valve；
It is servo-actuated that first is connected between the second pipeline of the first pipeline of revolution between revolution balanced valve and rotary motor and revolution
Shuttle valve, the output end of the first servo-actuated shuttle valve are connected with the first servo-actuated overflow valve, and the output end of the first servo-actuated overflow valve is connected to oil
Case is parallel with the second servo-actuated shuttle valve on the first servo-actuated shuttle valve, and the output end of the second servo-actuated shuttle valve connects fuel tank, and first is servo-actuated excessive
The X mouth of stream valve is connected with servo-actuated two logical pilot operated directional control valves, and it is servo-actuated excessive that servo-actuated two logical pilot operated directional control valves are connected with second
Valve is flowed, the output end of the second servo-actuated overflow valve connects oil return line L, is servo-actuated a wherein control terminal for two logical pilot operated directional control valves
Oil return line L is connected, another control terminal of servo-actuated two logical pilot operated directional control valves is connected to the end B of main servo-actuated solenoid directional control valve.
2. the main follow-up hydraulic system of small-sized fore-and-aft gangway according to claim 1, it is characterised in that: be connected on total output end
Main accumulator combination valve；Main accumulator combination valve includes accumulator two-position two-way hydraulic control reversal valve, accumulator bi-bit bi-pass electromagnetism
Reversal valve, accumulator overflow valve；Total output end is connected with accumulator, and total output end is connect with the input terminal of accumulator overflow valve,
The output end of accumulator overflow valve connects fuel tank；Total output end is connected to the end accumulator two-position two-way hydraulic control reversal valve P, accumulator
The end A connection rolling compensation system, pitch compensation system, telescopic system and the rotary system of two-position two-way hydraulic control reversal valve；Accumulation of energy
The end A and the end P of the wherein control terminal connection accumulator two-position two-way hydraulic control reversal valve of device two-position two-way hydraulic control reversal valve, accumulation of energy
The end A and the end P of another control terminal connection accumulator two-position two-way hydraulic control reversal valve of device two-position two-way hydraulic control reversal valve, accumulator two
Another control terminal of position two-way pilot operated directional control valve connects accumulator two-position two-way electromagnetic directional valve, and accumulator bi-bit bi-pass electromagnetism changes
Oil return line L is connected to valve.
3. the main follow-up hydraulic system of small-sized fore-and-aft gangway according to claim 1, it is characterised in that: in total output end and revolution electricity
Revolution pressure valve is equipped between proportional reversing valve, the X mouth for turning round pressure reducing valve is connected with the second shuttle valve, two input terminals point of the second shuttle valve
Not with revolution the first pipeline and turn round the second piping connection.
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| CN201811307435.5A CN109707681B (en) | 2018-11-05 | 2018-11-05 | Small-size step bridge owner follow-up hydraulic system |
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| CN201811307435.5A CN109707681B (en) | 2018-11-05 | 2018-11-05 | Small-size step bridge owner follow-up hydraulic system |
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| CN109707681B CN109707681B (en) | 2020-05-22 |
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Cited By (5)
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| CN111336139A (en) * | 2020-03-26 | 2020-06-26 | 厦门理工学院 | Hydraulic system and control method of ceramic brick press |
| CN112093673A (en) * | 2020-09-30 | 2020-12-18 | 安徽柳工起重机有限公司 | Crane control room movement mechanism and control method thereof |
| CN112922912A (en) * | 2021-02-03 | 2021-06-08 | 山东大学 | Wave compensation type closed rotary hydraulic control system for marine trestle |
| CN113479793A (en) * | 2021-07-05 | 2021-10-08 | 武汉船用机械有限责任公司 | Lifting hydraulic system |
| CN114215801A (en) * | 2021-11-09 | 2022-03-22 | 中船华南船舶机械有限公司 | Control method for rotary damping control hydraulic system |
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