CN110143271A - Pump control hydraulic steering engine - Google Patents
Pump control hydraulic steering engine Download PDFInfo
- Publication number
- CN110143271A CN110143271A CN201910246952.4A CN201910246952A CN110143271A CN 110143271 A CN110143271 A CN 110143271A CN 201910246952 A CN201910246952 A CN 201910246952A CN 110143271 A CN110143271 A CN 110143271A
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- Prior art keywords
- plunger
- oil
- valve
- pump
- hydraulic
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H25/00—Steering; Slowing-down otherwise than by use of propulsive elements; Dynamic anchoring, i.e. positioning vessels by means of main or auxiliary propulsive elements
- B63H25/06—Steering by rudders
- B63H25/08—Steering gear
- B63H25/14—Steering gear power assisted; power driven, i.e. using steering engine
- B63H25/18—Transmitting of movement of initiating means to steering engine
- B63H25/24—Transmitting of movement of initiating means to steering engine by electrical means
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H25/00—Steering; Slowing-down otherwise than by use of propulsive elements; Dynamic anchoring, i.e. positioning vessels by means of main or auxiliary propulsive elements
- B63H25/06—Steering by rudders
- B63H25/08—Steering gear
- B63H25/14—Steering gear power assisted; power driven, i.e. using steering engine
- B63H25/26—Steering engines
- B63H25/28—Steering engines of fluid type
- B63H25/30—Steering engines of fluid type hydraulic
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- Chemical & Material Sciences (AREA)
- Engineering & Computer Science (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a kind of pump control hydraulic steering engines, belong to steering engine field.Pump control hydraulic steering engine includes: base, steering mechanism, control unit, hydraulic station, and the first repairing unit, steering mechanism includes the first plunger cylinder, second plunger cylinder, plunger, tiller and rudder stock, the both ends of plunger are located in the first plunger cylinder and the second plunger cylinder, one end of tiller is connect with plunger, and one end of tiller is between the first plunger cylinder and the second plunger cylinder, rudder stock is set to the other end of tiller, rudder stock is for driving rudder blade to rotate, hydraulic station includes first motor, first hydraulic pump and driving valve group, first motor is for driving the rotation of the first hydraulic pump, first hydraulic pump includes the first pump ontology, the first actuator port and the second actuator port on the first pump ontology, first actuator port is connected to by driving valve group and the first plunger cylinder without plunger cavity, second actuator port passes through driving valve Group is connected to the second plunger cylinder without plunger cavity.
Description
Technical field
The present invention relates to steering engine field, in particular to a kind of pump control hydraulic steering engine.
Background technique
Using hydraulic oil as working media, ship can be made to come about and the device of rudder position is kept to be known as hydraulic sterring engine.Hydraulic rudder
The working principle of machine is that pump exports high pressure oil driving rudder blade rotation under motor driven.Not according to steering engine steering control modes
Together, hydraulic sterring engine can be divided into valve control hydraulic sterring engine and pump control hydraulic steering engine.The difference of the two is that valve control hydraulic sterring engine is logical
The direction of the high pressure oil of reversal valve control pump output is crossed, and then realizes the switching operation of rudder blade；Pump control hydraulic steering engine is to pass through electricity
Machine controls the direction that small pump positive and negative rotation adjusts the high pressure oil of small pump output, and then realizes the switching operation of rudder blade.
Traditional pump control hydraulic steering engine generally uses La Puxun-fork type structure, mainly includes tiller, plunger, oil cylinder, change
Amount pump and pump control device, working principle include: to issue rudder angle instruction by steering stand, control device by pump, make in variable pump tiltedly
Disk inclination, and then into row pressure oil；Pressure oil pushes the translation of oil cylinder inner plunger, and plunger drives tiller rotary motion；Tiller will turn
It is dynamic to pass to rudder stock and rudder blade, realize the steering of ship.
In the implementation of the present invention, the inventor finds that the existing technology has at least the following problems: one end of tiller is logical
It crosses plunger pin and idler wheel is connect with plunger, the other end is hung and rudder stock is fixed on the other end of tiller, since the other end is born
The dual gravity of tiller and rudder stock, therefore tiller stability in rotation is poor.
Summary of the invention
The embodiment of the invention provides a kind of pump control hydraulic steering engines, can guarantee the stability of tiller rotation.The technology
Scheme is as follows:
The present invention provides a kind of pump control hydraulic steering engine, the pump control hydraulic steering engine includes: base, steering mechanism, control
Unit, hydraulic station and the first repairing unit, the steering mechanism include the first plunger cylinder, the second plunger cylinder, plunger,
Tiller and rudder stock, the both ends of the plunger are located in first plunger cylinder and second plunger cylinder, the rudder
One end of handle is connect with the plunger and one end of the tiller is located at first plunger cylinder and second plunger cylinder
Between, the rudder stock is set to the other end of the tiller, and for the rudder stock for driving rudder blade to rotate, the hydraulic station includes first
Motor, the first hydraulic pump and driving valve group, for the first motor for driving first hydraulic pump to rotate, described first is hydraulic
Pump includes the first pump ontology, the first actuator port and the second actuator port on the first pump ontology, first work
Make hydraulic fluid port being connected to without plunger cavity by driving valve group and first plunger cylinder, second actuator port passes through institute
Being connected to without plunger cavity for driving valve group and second plunger cylinder is stated, the first repairing unit includes piston oil-cylinder, second
Motor, the second hydraulic pump, pressure-regulating valve group and fuel tank, the piston oil-cylinder are fixed on the base, in the piston oil-cylinder
Equipped with piston rod, it is outer and connect with the other end of the tiller that the piston oil-cylinder is stretched out in one end of the piston rod, and described the
For driving second hydraulic pump to rotate, second hydraulic pump includes the second pump ontology, is set to second pump two motors
Third actuator port and the 4th actuator port on ontology, the third actuator port by the pressure-regulating valve group with it is described
The rodless cavity of piston oil-cylinder is connected to, and the 4th actuator port is connected to the fuel tank.
Optionally, the pressure-regulating valve group includes: that the first decompression overflow valve and second depressurize overflow valve,
The first decompression overflow valve includes the first valve body, the first oil inlet on first valve body, the
One oil outlet and the first drain tap, the second decompression overflow valve includes the second valve body, on second valve body
Second oil inlet, the second oil outlet and the second drain tap,
First oil inlet of the first decompression overflow valve respectively with the third actuator port of second hydraulic pump, described
The rodless cavity connection of the second oil inlet and the piston oil-cylinder of second decompression overflow valve, the second decompression overflow valve
Second oil inlet is connected to the rodless cavity of the third actuator port of second hydraulic pump and the piston oil-cylinder respectively, institute
State the second oil outlet, the Yi Ji of the first oil outlet of the first decompression overflow valve, the first drain tap, the second decompression overflow valve
Two drain taps are connected to the fuel tank respectively.
Optionally, the pressure-regulating valve group further includes reversal valve,
The second oil inlet difference of first oil inlet of the first decompression overflow valve and the second decompression overflow valve
It is connected to by the reversal valve with the rodless cavity of the piston oil-cylinder.
Optionally, it overflows between the first oil outlet and the fuel tank of the first decompression overflow valve with second decompression
It flows between the second oil outlet and the fuel tank of valve, be equipped with filter.
Optionally, the pump control hydraulic steering engine further includes the second repairing unit,
The second repairing unit includes the first Fill valve and the second Fill valve, and first Fill valve and described second are mended
The oil inlet of oil valve is connected to the fuel tank, the oil outlet of first Fill valve respectively with first hydraulic pump first
Actuator port is connected to first plunger cylinder without plunger cavity, and the oil outlet of second Fill valve is respectively and with described
Second actuator port of one hydraulic pump is connected to second plunger cylinder without plunger cavity.
Optionally, the driving valve group includes off-load solenoid valve, and the oil outlet and the fuel tank of the off-load solenoid valve connect
It is logical, the oil inlet of the off-load solenoid valve respectively with the first actuator port of first hydraulic pump, first plunger cylinder
Being connected to without plunger cavity without plunger cavity and second plunger cylinder.
Optionally, the driving valve group includes bidirectional relief valve, the first hydraulic fluid port of the bidirectional relief valve respectively with it is described
First actuator port of the first hydraulic pump is connected to first plunger cylinder without plunger cavity, and the second of the bidirectional relief valve
Hydraulic fluid port is connected to the second actuator port of first hydraulic pump and second plunger cylinder without plunger cavity respectively.
Optionally, the first motor is variable-frequency motor.
Optionally, first hydraulic pump is constant displacement pump.
Optionally, described control unit is used for,
Reception is come about instruction, and the instruction of coming about includes target rudder angle；
Based on the target rudder angle, the revolving speed and rotation direction of the first motor are adjusted.
Technical solution provided in an embodiment of the present invention has the benefit that the first working oil by the first hydraulic pump
Mouthful be connected to without plunger cavity by driving valve group and the first plunger cylinder, the second actuator port is by driving valve group and the second plunger
Oil cylinder is connected to without plunger cavity, in this way, the first hydraulic pump is rotated by first motor, passes through driving valve group conveying high-pressure oil
To the first plunger cylinder and the second plunger cylinder and plunger is pushed to be translatable, plunger drives tiller rotation, and tiller again transmits rotation
Coming about for ship is realized by rudder stock driving rudder blade rotation to rudder stock；Piston rod is equipped in piston oil-cylinder, one end of piston rod is stretched
Piston oil-cylinder is outer out and connect with the other end of tiller, in this way, when plunger is mobile and drives piston rod movement so that piston oil-cylinder
Rodless cavity space when becoming smaller, extra oil liquid flows back to fuel tank by pressure-regulating valve group in the first repairing unit；And work as plunger
When mobile and drive piston rod movement is so that the rodless cavity space of piston oil-cylinder becomes larger, the second motor and the second hydraulic pump will be passed through
By pressure-regulating valve group to piston oil-cylinder repairing；Under both situations, since piston rod is intended to overcome the pressure of pressure oil to move
Dynamic, therefore, piston rod will react on plunger, so that plunger movement speed tends to a certain range, the stabilization for keeping plunger mobile
Property, rudder stock balanced action is played, guarantees the stability of tiller rotation.
Detailed description of the invention
To describe the technical solutions in the embodiments of the present invention more clearly, make required in being described below to embodiment
Attached drawing is briefly described, it should be apparent that, drawings in the following description are only some embodiments of the invention, for
For those of ordinary skill in the art, without creative efforts, it can also be obtained according to these attached drawings other
Attached drawing.
Fig. 1 is a kind of structural schematic diagram of pump control hydraulic steering engine provided in an embodiment of the present invention.
In attached drawing, 1 base, 2 steering mechanisms, 21 first plunger cylinders, 22 second plunger cylinders, 23 plungers, 24 tillers, 25
Rudder stock, 3 hydraulic stations, 31 first motors, 32 first hydraulic pumps, 33 driving valve groups, 33a off-load solenoid valve, 33b bidirectional relief valve, 4
First repairing unit, 41 piston oil-cylinders, 42 second motors, 43 second hydraulic pumps, 44 pressure-regulating valve groups, 45 fuel tanks, 44a first
Depressurize overflow valve, 44b second depressurize overflow valve, 44c reversal valve, 44d filter, 5 second repairing units, 51 first Fill valves,
52 second Fill valves.
Specific embodiment
To make the object, technical solutions and advantages of the present invention clearer, below in conjunction with attached drawing to embodiment party of the present invention
Formula is described in further detail.
In traditional pump control hydraulic steering engine, motor generally selects asynchronous machine, and hydraulic pump generally selects variable pump, and uses
Volumetric speed control mode adjusts pump speed, and which has the disadvantage in that
The first, suction capacity declines when oil pump low speed is run, and forms cavitation erosion, noise, flow pulse etc. and steering engine is caused to run
It is unstable.
The second, the rapidity of asynchronous machine inertia larger impact instruction response.
Third, speed adjustable range are limited, are limited by variable pump swash plate pivot angle amplitude.
4th, during the small flow hydraulic oil of suction, for variable pump still in the state of running at high speed, noise is larger, motor effect
Rate changes with load and is changed, and system effectiveness is low.
Fig. 1 shows a kind of pump control hydraulic steering engine provided in an embodiment of the present invention.Referring to Fig. 1, the pump control hydraulic steering engine packet
It includes: base 1, steering mechanism 2, control unit (not shown go out), hydraulic station 3 and the first repairing unit 4.
Steering mechanism 2 includes the first plunger cylinder 21, the second plunger cylinder 22, plunger 23, tiller 24 and rudder stock；Plunger 23
Both ends be located in the first plunger cylinder 21 and the second plunger cylinder 22, one end of tiller 24 is connect with plunger 23 and rudder
Between the first plunger cylinder 21 and the second plunger cylinder 22, rudder stock is set to the other end of tiller 24, rudder stock for one end of handle 24
For driving rudder blade to rotate.
Hydraulic station 3 includes first motor 31, the first hydraulic pump 32 and driving valve group 33；First hydraulic pump 32 includes the first pump
Ontology, the first actuator port and the second actuator port on the first pump ontology, the first actuator port pass through driving valve group 33
The nothing for passing through driving valve group 33 and the second plunger cylinder 22 with being connected to without plunger cavity for the first plunger cylinder 21, the second actuator port
Plunger cavity connection.
First repairing unit 4 includes piston oil-cylinder 41, the second motor 42, the second hydraulic pump 43,44 and of pressure-regulating valve group
Fuel tank 45；Piston oil-cylinder 41 is fixed on base 1, and piston rod is equipped in piston oil-cylinder 41, and piston oil-cylinder is stretched out in one end of piston rod
It is connect outside 41 and with the other end of tiller 24, the second motor 42 is for driving the rotation of the second hydraulic pump 43, the second hydraulic pump 43 packet
The second pump ontology, third actuator port and the 4th actuator port on the second pump ontology are included, third actuator port passes through pressure
Force regulating valve group 44 is connected to the rodless cavity of piston oil-cylinder 41, and the 4th actuator port is connected to fuel tank 45.
Specifically, one end of tiller 24 is connect, plunger pin and rolling by plunger pin and idler wheel (not shown go out) with plunger 23
The movement of plunger 23 is changed into the rotary motion of idler wheel by wheel, and tiller 24 is driven to rotate.
By the first actuator port of the first hydraulic pump 32 by driving valve group 33 and the first plunger cylinder 21 without plunger
Chamber connection, the second actuator port is connected to by driving valve group 33 and the second plunger cylinder 22 without plunger cavity, in this way, first is hydraulic
Pump 32 is rotated by first motor 31, passes through driving 33 conveying high-pressure oil of valve group to the first plunger cylinder 21 and the second plunger
Oil cylinder 22 simultaneously pushes plunger 23 to be translatable, and plunger 23 drives tiller 24 to rotate, and rotation is passed to rudder stock again, driven by rudder stock by tiller 24
Dynamic rudder blade rotation, realizes coming about for ship；Piston rod is equipped in piston oil-cylinder 41, one end of piston rod is stretched out outside piston oil-cylinder 41
And connect with the other end of tiller 24, in this way, when plunger 23 is mobile and drive piston rod mobile so that piston oil-cylinder 41 without bar
When cavity space becomes smaller, extra oil liquid flows back to fuel tank 45 by pressure-regulating valve group 44 in the first repairing unit 4；And work as plunger 23
When mobile and drive piston rod movement is so that the rodless cavity space of piston oil-cylinder 41 becomes larger, the second motor 42 and the second liquid will be passed through
Press pump 43 passes through pressure-regulating valve group 44 to 41 repairing of piston oil-cylinder；Under both situations, since piston rod is intended to overcome pressure
The pressure of oil is mobile, and therefore, piston rod will react on plunger 23, so that 23 movement speed of plunger tends to a certain range, keeps
The mobile stability of plunger 23, plays rudder stock balanced action, guarantees the stability that tiller 24 rotates.
Illustratively, first motor 31 is variable-frequency motor.Firstly, variable-frequency motor can will not generate electric current punching with frequent start-stop
It hits, can be shut down in the case where not needing operation, improve the safety of steering engine.Secondly, the inertia of variable-frequency motor is less than asynchronous
The inertia of motor, will more quickly in the instruction of response control unit.
Illustratively, the first hydraulic pump 32 is constant displacement pump.Constant displacement pump is compared with variable pump, high reliablity and to system environments
Adaptable, the noise of constant displacement pump is also smaller.
In hydraulic station 3, illustratively, referring to Fig. 1, driving valve group 33 includes off-load solenoid valve 33a.Off-load solenoid valve 33a
Oil outlet be connected to fuel tank 45, the oil inlet of off-load solenoid valve 33a respectively with the first actuator port of the first hydraulic pump 32,
Being connected to without plunger cavity without plunger cavity and the second plunger cylinder 22 of one plunger cylinder 21.Wherein, off-load solenoid valve 33a is used for
It is opened and closed under the instruction of control unit.When off-load solenoid valve 33a is opened, the oil inlet of off-load solenoid valve 33a and fuel-displaced
Mouth disconnects, and at this moment hydraulic oil passes through off-load solenoid valve 33a inflow fuel tank 45 in oil circuit；When off-load solenoid valve 33a is closed, off-load
The oil inlet of solenoid valve 33a is connected to oil outlet, and at this moment hydraulic oil cannot flow into fuel tank by off-load solenoid valve 33a in oil circuit
45。
The course of work of hydraulic station 3 includes: that control unit receives instruction of coming about, which includes target rudder angle；Control
Unit processed is based on target rudder angle, adjusts the revolving speed and rotation direction of first motor 31.Specifically, control unit is based on target rudder
Angle and current rudder angle adjust the revolving speed and rotation direction of first motor 31.First motor 31 drives the first hydraulic pump 32 fortune
Turn, control unit synchronously control off-load solenoid valve 33a is opened, and off-load solenoid valve 33a will be switched off off-load solenoid valve 33a's after opening
The oil liquid of oil inlet and oil outlet, i.e. relief circuit between cutting hydraulic station 3 and fuel tank 45, the discharge of the first hydraulic pump 32 passes through
The movement of plunger 23 is controlled the rotation direction of rudder blade by the direction of motion of rudder stock, and then controls the direction of motion of ship.When
When control unit detects that current rudder angle reaches target rudder angle, control unit will reduce the revolving speed of first motor 31, and then drive
The revolving speed of first hydraulic pump 32 declines, and system oil mass is reduced, and plunger 23 will stop swinging.
Optionally, referring to Fig. 1, driving valve group 33 further includes bidirectional relief valve 33b.The first hydraulic fluid port of bidirectional relief valve 33b
It is connected to respectively with the first actuator port of the first hydraulic pump 32 and the first plunger cylinder 21 without plunger cavity, bidirectional relief valve 33b
The second hydraulic fluid port be connected to respectively with the second actuator port of the first hydraulic pump 32 and the second plunger cylinder 22 without plunger cavity.Its
In, bidirectional relief valve 33 is the oil guaranteed when oil circuit oil liquid passes in and out the first plunger cylinder 21 and the second plunger cylinder 22 and commutation
Pressure safety.Specifically, after the empty hydraulic sterring engine of pump starts starting, the first hydraulic fluid port of bidirectional relief valve 33b is not connect with the second hydraulic fluid port
Logical state.Assuming that hydraulic oil is discharged in the first actuator port of the first hydraulic pump 32, at this moment, when the first oil of bidirectional relief valve 33b
When the pressure of mouth reaches goal pressure, the second hydraulic fluid port of bidirectional relief valve 33b will be connected to discharge target flow with the first hydraulic fluid port
Hydraulic oil reduces hydraulic fluid pressure in oil circuit；Assuming that hydraulic oil is discharged in the second actuator port of the first hydraulic pump 32, at this moment, when
When the pressure of the second hydraulic fluid port of bidirectional relief valve 33b reaches goal pressure, the second hydraulic fluid port of bidirectional relief valve 33b will be with the first oil
The hydraulic oil of mouth connection discharge target flow, reduces hydraulic fluid pressure in oil circuit.
Wherein, pressure-regulating valve group 44 is used to control the pressure value of piston oil-cylinder 41, keeps tiller 24 to rotate with this steady
It is qualitative, prevent cavitation erosion or hypertonia.Illustratively, in the first repairing unit 4, referring to Fig. 1, pressure-regulating valve group 44 is wrapped
It includes: the first decompression overflow valve 44a and the second decompression overflow valve 44b.First decompression overflow valve 44a includes the first valve body, is set to
The first oil inlet, the first oil outlet and the first drain tap on first valve body, the second decompression overflow valve 44b includes the second valve sheet
Body, the second oil inlet on the second valve body, the second oil outlet and the second drain tap.The of first decompression overflow valve 44a
One oil inlet depressurizes the second oil inlet of overflow valve 44b respectively and is lived with the third actuator port of the second hydraulic pump 43, second
Fill in the rodless cavity connection of oil cylinder 41.The second oil inlet third work with the second hydraulic pump 43 respectively of second decompression overflow valve 44b
Make the rodless cavity connection of hydraulic fluid port and piston oil-cylinder 41.First decompression the first oil outlet of overflow valve 44a, the first drain tap, the
The second oil outlet and the second drain tap of two decompression overflow valve 44b is connected to fuel tank 45 respectively.Wherein, the first decompression overflow
The decompression of valve 44a and second overflow valve 44b is a kind of hydraulic pressure control valve, plays level pressure overflow in hydraulic device, is
System off-load and safeguard protection effect.Such as: in constant displacement pump (the second hydraulic pump 43) flow reduction conditions system, constant displacement pump provides perseverance
Fixed flow can be such that flow demand reduces when system pressure increases.Excess traffic is protected by the excessive oil return box of overflow valve at this time
Demonstrate,prove system pressure.Specifically, by first decompression overflow valve 44a for, first decompression overflow valve 44a the first oil inlet oil inlet and
Input pressure is indefinite, and the first oil outlet is fuel-displaced and oil pressure is constant (in target zone) out, and the first drain tap is adjusted for being discharged
Oil after input pressure.
Wherein, when plunger 23 is mobile and drives piston rod movement so that the rodless cavity space of piston oil-cylinder 41 becomes smaller, the
Extra oil liquid flows back to fuel tank 45 by pressure-regulating valve group 44 in one repairing unit 4；And when the movement of plunger 23 and with piston
When bar movement is so that the rodless cavity space of piston oil-cylinder 41 becomes larger, pressure will be passed through by the second motor 42 and the second hydraulic pump 43
Valve group 44 is adjusted to 41 repairing of piston oil-cylinder；Under both situations, since piston rod is intended to overcome the pressure of pressure oil mobile, because
This, piston rod will react on plunger 23, so that 23 movement speed of plunger tends to a certain range, the stabilization for keeping plunger 23 mobile
Property.
Specifically, the first decompression overflow valve 44a and the second decompression overflow valve 44b is that the Direct Action Type of carry potential overflow valve function subtracts
Pressure valve.
Illustratively, referring to Fig. 1, pressure-regulating valve group 44 further includes reversal valve 44c.The of first decompression overflow valve 44a
The second oil inlet of one oil inlet and the second decompression overflow valve 44b pass through reversal valve 44c with piston oil-cylinder 41 without bar respectively
Chamber connection.Wherein, reversal valve 44c is to change oil circuit in valve by changing different positions, so that outlet oil circuit is different, is risen
It is acted on to commutation.
It should be noted that the oil circuit between reversal valve 44c and the rodless cavity of piston oil-cylinder 41 is also connected with an oil circuit (figure
One end of the oil circuit is connectionless in 1), which can be connected to fuel tank 45, for adjustable change valve 44c and piston oil-cylinder 41
Pressure between rodless cavity.
Illustratively, it referring to Fig. 1, is depressurized between the first oil outlet and fuel tank 45 of the first decompression overflow valve 44a with second
Between the second oil outlet and fuel tank 45 of overflow valve 44b, it is equipped with filter 44d.Filter 44d is used for the oil for draining into fuel tank 45
Liquid is filtered, and removes impurity.
Wherein, steering engine drives mainly by hydraulic oil and moves, and playing inside steering engine equipped with sealing element prevents hydraulic fluid leak
Effect, still, due to the aging of sealing element, the aging of valve member, the work pieces process such as plunger 23, valve group face is of poor quality, can all cause
The leakage of hydraulic oil.The leakage of hydraulic oil is creeped when will lead to steering engine work, is vibrated and phenomena such as noise.In order to solve this
Problem, illustratively, pump control hydraulic steering engine further include the second repairing unit 5.Second repairing unit 5 includes 51 He of the first Fill valve
Second Fill valve 52.The oil inlet of first Fill valve 51 and the second Fill valve 52 is connected to fuel tank 45, the first Fill valve 51
Oil outlet is connected to the first actuator port of the first hydraulic pump 32 and the first plunger cylinder 21 without plunger cavity respectively, the second repairing
The oil outlet of valve 52 is connected to with the second actuator port of the first hydraulic pump 32 and the second plunger cylinder 22 without plunger cavity respectively.
By the first Fill valve 51 and the second Fill valve 52 to 32 repairing of the first hydraulic pump, the first hydraulic pump 32 can be avoided
Suction capacity declines when low speed is run, and avoids the formation of cavitation erosion, noise, flow pulse etc. and cause steering engine fluctuation of service.In addition,
The big reason of variable pump noise, greatly the reason is that fluid noise.The fluid noise of hydraulic pump is mainly the pressure pumped, stream
Caused by measuring cyclically-varying and cavitation.In this way, while avoiding the formation of cavitation erosion, noise, flow pulse, moreover it is possible to reduce stream
Bulk noise, and then reduce Noice of Hydraulic Pumps.
Illustratively, control unit is used for, and when rudder angle reaches target rudder angle, the revolving speed of control first motor 31 is 0.With
This saves energy loss.
In the present embodiment, hydraulic station 3 is Closed Hydraulic station 3, and closed system is more energy saving relative to open system, because
Its working connection, without other valves such as reversal valve 44c, reduces crushing in addition to hydraulic lock.Closed Hydraulic station 3 combines variable-frequency motor skill
Art, compared with conventional valve control, pump control system steering engine, frequency conversion steering gear system is simple, sensitive, can be reversed variable-frequency motor with it is hydraulic
Two-way oil pump cooperates flow in regulating system, controls the revolving speed of steering engine, realizes the stepless time adjustment of discharge capacity, guarantees plunger 23 in oil cylinder
It is steady to push, guarantee steering engine operation stability and efficiency.
The foregoing is merely presently preferred embodiments of the present invention, is not intended to limit the invention, it is all in spirit of the invention and
Within principle, any modification, equivalent replacement, improvement and so on be should all be included in the protection scope of the present invention.
Claims (10)
1. a kind of pump control hydraulic steering engine, which is characterized in that the pump control hydraulic steering engine includes: base (1), steering mechanism (2), control
Unit, hydraulic station (3) and the first repairing unit (4) processed, the steering mechanism (2) include the first plunger (23) oil cylinder (21),
The both ends of second plunger (23) oil cylinder (22), plunger (23), tiller (24) and rudder stock (25), the plunger (23) are located at institute
It states in the first plunger (23) oil cylinder (21) and second plunger (23) oil cylinder (22), one end of the tiller (24) and the column
One end of plug (23) connection and the tiller (24) is located at the first plunger (23) oil cylinder (21) and second plunger (23)
Between oil cylinder (22), the rudder stock (25) is set to the other end of the tiller (24), and the rudder stock (25) is for driving rudder blade to revolve
Turn, the hydraulic station (3) includes first motor (31), the first hydraulic pump (32) and driving valve group (33), the first motor
(31) for driving first hydraulic pump (32) to rotate, first hydraulic pump (32) includes the first pump ontology, set on described
The first actuator port and the second actuator port on first pump ontology, first actuator port pass through the driving valve group (33)
With being connected to without plunger (23) chamber for the first plunger (23) oil cylinder (21), second actuator port passes through the driving valve group
(33) it is connected to the second plunger (23) oil cylinder (22) without plunger (23) chamber, the first repairing unit (4) includes piston
Oil cylinder (41), the second motor (42), the second hydraulic pump (43), pressure-regulating valve group (44) and fuel tank (45), the piston oil-cylinder
(41) it is fixed on the base (1), piston rod is equipped in the piston oil-cylinder (41), the work is stretched out in one end of the piston rod
Plug oil cylinder (41) connect outside and with the other end of the tiller (24), and second motor (42) is used to drive described second hydraulic
(43) rotation is pumped, second hydraulic pump (43) includes the second pump ontology, the third working oil on the second pump ontology
Mouth and the 4th actuator port, the third actuator port pass through the pressure-regulating valve group (44) and the piston oil-cylinder (41)
Rodless cavity connection, the 4th actuator port are connected to the fuel tank (45).
2. pump control hydraulic steering engine according to claim 1, which is characterized in that the pressure-regulating valve group (44) includes:
One decompression overflow valve (44a) and the second decompression overflow valve (44b),
First decompression overflow valve (44a) includes the first valve body, the first oil inlet on first valve body, the
One oil outlet and the first drain tap, second decompression overflow valve (44b) include the second valve body, are set to second valve body
On the second oil inlet, the second oil outlet and the second drain tap,
The first oil inlet third working oil with second hydraulic pump (43) respectively of first decompression overflow valve (44a)
The rodless cavity connection of mouth, the second oil inlet of second decompression overflow valve (44b) and the piston oil-cylinder (41), it is described
The second oil inlet third actuator port, Yi Jisuo with second hydraulic pump (43) respectively of second decompression overflow valve (44b)
State the rodless cavity connection of piston oil-cylinder (41), the first oil outlet, the first drain tap, institute of first decompression overflow valve (44a)
The second oil outlet and the second drain tap for stating the second decompression overflow valve (44b) are connected to the fuel tank (45) respectively.
3. pump control hydraulic steering engine according to claim 2, which is characterized in that the pressure-regulating valve group (44) further includes changing
To valve (44c),
Second oil inlet of the first oil inlet of first decompression overflow valve (44a) and second decompression overflow valve (44b)
Mouth is connected to by the reversal valve (44c) with the rodless cavity of the piston oil-cylinder (41) respectively.
4. pump control hydraulic steering engine according to claim 3, which is characterized in that the of first decompression overflow valve (44a)
Between one oil outlet is connected to the fuel tank (45) and it is described second decompression overflow valve (44b) the second oil outlet and the oil
Between case (45) connection, it is equipped with filter (44d).
5. pump control hydraulic steering engine according to claim 1, which is characterized in that the pump control hydraulic steering engine further includes the second benefit
Oily unit (5),
The second repairing unit (5) includes the first Fill valve (51) and the second Fill valve (52),
The oil inlet of first Fill valve (51) and second Fill valve (52) is connected to the fuel tank (45), and described
The oil outlet of one Fill valve (51) respectively with the first actuator port and first plunger (23) of first hydraulic pump (32)
Oil cylinder (21) without plunger (23) chamber be connected to, the oil outlet of second Fill valve (52) respectively with first hydraulic pump
(32) the second actuator port is connected to the second plunger (23) oil cylinder (22) without plunger (23) chamber.
6. pump control hydraulic steering engine according to claim 5, which is characterized in that the driving valve group (33) includes off-load electromagnetism
The oil outlet of valve (33a), the off-load solenoid valve (33a) is connected to the fuel tank (45), the off-load solenoid valve (33a) into
Hydraulic fluid port respectively with the first actuator port of first hydraulic pump (32), first plunger (23) oil cylinder (21) without plunger
(23) chamber and the second plunger (23) oil cylinder are connected to without plunger (23) chamber.
7. pump control hydraulic steering engine according to claim 6, which is characterized in that the driving valve group (33) further includes two-way peace
Full valve (33b), the first hydraulic fluid port of the bidirectional relief valve (33b) the first actuator port with first hydraulic pump (32) respectively
With being connected to without plunger (23) chamber for the first plunger (23) oil cylinder (21), the second hydraulic fluid port point of the bidirectional relief valve (33b)
Not with the second actuator port of first hydraulic pump (32) and second plunger (23) oil cylinder (22) without plunger (23) chamber
Connection.
8. pump control hydraulic steering engine described in any one of -7 according to claim 1, which is characterized in that the first motor (31) is
Variable-frequency motor.
9. pump control hydraulic steering engine according to claim 8, which is characterized in that first hydraulic pump (32) is constant displacement pump.
10. pump control hydraulic steering engine described in any one of -7 according to claim 1, which is characterized in that described control unit is used for,
Reception is come about instruction, and the instruction of coming about includes target rudder angle；
Based on the target rudder angle, the revolving speed and rotation direction of the first motor (31) are adjusted.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910246952.4A CN110143271B (en) | 2019-03-29 | 2019-03-29 | Pump-controlled hydraulic steering engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910246952.4A CN110143271B (en) | 2019-03-29 | 2019-03-29 | Pump-controlled hydraulic steering engine |
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| Publication Number | Publication Date |
|---|---|
| CN110143271A true CN110143271A (en) | 2019-08-20 |
| CN110143271B CN110143271B (en) | 2021-04-30 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201910246952.4A Active CN110143271B (en) | 2019-03-29 | 2019-03-29 | Pump-controlled hydraulic steering engine |
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| CN (1) | CN110143271B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115087593A (en) * | 2020-02-28 | 2022-09-20 | 川崎重工业株式会社 | Steering system |
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| GB734621A (en) * | 1953-02-09 | 1955-08-03 | Mactaggart Scott And Company L | Improvements in and relating to means for the remote control of ships' steering gear and other apparatus |
| JPS6020996U (en) * | 1983-07-22 | 1985-02-13 | 横河電機株式会社 | steering gear |
| JPS6021353Y2 (en) * | 1984-03-27 | 1985-06-25 | 株式会社トキメック | Steering control device |
| CN1123242A (en) * | 1994-10-10 | 1996-05-29 | 大连海事大学 | Unbalanced helming driving-torque imitating device |
| CN202226052U (en) * | 2011-08-16 | 2012-05-23 | 无锡市东舟船舶附件有限公司 | Frequency-conversion valve-controlled hydraulic system of steering engine for ship |
| CN108778925A (en) * | 2016-02-22 | 2018-11-09 | 三菱重工业株式会社 | Hydraulic steering gear and ship |
| CN208348187U (en) * | 2018-05-08 | 2019-01-08 | 凌云工业股份有限公司 | A kind of hydraulic press hydraulic control system equipped with synchronized cylinder |
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2019
- 2019-03-29 CN CN201910246952.4A patent/CN110143271B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB734621A (en) * | 1953-02-09 | 1955-08-03 | Mactaggart Scott And Company L | Improvements in and relating to means for the remote control of ships' steering gear and other apparatus |
| JPS6020996U (en) * | 1983-07-22 | 1985-02-13 | 横河電機株式会社 | steering gear |
| JPS6021353Y2 (en) * | 1984-03-27 | 1985-06-25 | 株式会社トキメック | Steering control device |
| CN1123242A (en) * | 1994-10-10 | 1996-05-29 | 大连海事大学 | Unbalanced helming driving-torque imitating device |
| CN202226052U (en) * | 2011-08-16 | 2012-05-23 | 无锡市东舟船舶附件有限公司 | Frequency-conversion valve-controlled hydraulic system of steering engine for ship |
| CN108778925A (en) * | 2016-02-22 | 2018-11-09 | 三菱重工业株式会社 | Hydraulic steering gear and ship |
| CN208348187U (en) * | 2018-05-08 | 2019-01-08 | 凌云工业股份有限公司 | A kind of hydraulic press hydraulic control system equipped with synchronized cylinder |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115087593A (en) * | 2020-02-28 | 2022-09-20 | 川崎重工业株式会社 | Steering system |
| CN115087593B (en) * | 2020-02-28 | 2024-02-09 | 川崎重工业株式会社 | Steering system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110143271B (en) | 2021-04-30 |
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