CN104358722B - A kind of ocean engineering crane hydraulic control system - Google Patents
A kind of ocean engineering crane hydraulic control system Download PDFInfo
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- CN104358722B CN104358722B CN201410627473.4A CN201410627473A CN104358722B CN 104358722 B CN104358722 B CN 104358722B CN 201410627473 A CN201410627473 A CN 201410627473A CN 104358722 B CN104358722 B CN 104358722B
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- 239000012530 fluid Substances 0.000 claims abstract description 159
- 239000003921 oil Substances 0.000 claims abstract description 99
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 74
- 230000008859 change Effects 0.000 claims description 15
- 230000007246 mechanism Effects 0.000 claims description 5
- 238000006073 displacement reaction Methods 0.000 claims description 4
- 239000013589 supplement Substances 0.000 abstract description 2
- 241000269799 Perca fluviatilis Species 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 230000000977 initiatory effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000008450 motivation Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000011897 real-time detection Methods 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
- B66C23/18—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes
- B66C23/36—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes mounted on road or rail vehicles; Manually-movable jib-cranes for use in workshops; Floating cranes
- B66C23/52—Floating cranes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a kind of ocean engineering crane hydraulic control system, belong to ocean engineering crane technical field, main motor is connected with main pump group, the oil-out of main pump group is connected with the oil inlet of commutation valve group, first oil-out of the valve group that commutates, second oil-out is connected by balancing valve group with two hydraulic fluid ports of hydraulic motor respectively, the oil return opening of the valve group that commutates is connected with the oil inlet of main pump group, hydraulic control system also includes repairing motor, slippage pump and hydraulic oil container, repairing motor is connected with slippage pump, the oil inlet of slippage pump is connected with the oil-out of hydraulic oil container, the oil-out of slippage pump is connected with the oil inlet of main pump group, the first check valve is provided with the pipeline that the oil return opening of hydraulic oil container is connected and connected with the oil return opening of commutation valve group.It is connected with slippage pump by by repairing motor, slippage pump can fully supplement hydraulic oil, the first check valve can produce certain back pressure when hydraulic oil is full of in fluid pressure line, increase main pump group suction capacity, prevent main pump group to be emptied and vibrate.
Description
Technical field
The present invention relates to ocean engineering crane technical field, more particularly to a kind of ocean engineering crane hydraulic control system
System.
Background technology
The lifting mechanisms such as crane, the hydraulic control of crane are often used in the engineering equipment of ship and ocean platform
System is sufficiently complex, and the design rationality of crane hydraulic system directly influences the use longevity of associated component in hydraulic system
Life.
The hydraulic system of ocean engineering crane is generally required and uses large-flow hydraulic system, large-flow hydraulic system work
When need the volumetric ratio of hydraulic oil container that matching is used larger, the hydraulic oil in the fluid pressure line of such hydraulic system could run
Smoothness, however the equipment of extra large work crane in the arrangement of space closely due to, cause that hydraulic oil container is designed to ratio again
It is smaller；Meanwhile, because offshore engineering equipment needs to be worked in wind speed is than larger ocean, it is contemplated that wind-force is to hydraulic oil container
Influence and to the maintenance convenience of hydraulic oil container, hydraulic oil container will not generally perch.
However, realize it is of the invention during, inventor find prior art at least there is problems with：
In the hydraulic system of the big flow of existing ocean engineering crane, because the volume of hydraulic oil container is typically designed
It is smaller, and the putting position of hydraulic oil container is relatively low, so that the precompression that the hydraulic oil at the inlet port of pump group possesses
Deficiency, when pump group runs at high speed work, easily causes that pump group oil suction is not smooth, the fluid pressure line at the inlet port of pump group
In easily form negative pressure, easily there is air pocket, cavitation at the inlet port of pump group under the negative pressure condition, make the service life of pump group
Substantially reduce, while also result in whole hydraulic system and vibrating and producing larger noise.
The content of the invention
In order to solve problem of the prior art, a kind of ocean engineering crane hydraulic control system is the embodiment of the invention provides
System, technical scheme is as follows：
A kind of ocean engineering crane hydraulic control system is the embodiment of the invention provides, the hydraulic control system includes
Main motor, main pump group, commutation valve group, balance valve group, hydraulic motor, the main motor are connected with the main pump group, the main pump
The oil-out of group is connected with the oil inlet of the commutation valve group, the first oil-out of the commutation valve group, the second oil-out difference
Connected with two hydraulic fluid ports of the hydraulic motor by the balance valve group, the oil return opening and the main pump group of the commutation valve group
Oil inlet connection, the hydraulic control system also include repairing motor, slippage pump and hydraulic oil container,
The repairing motor is connected with the slippage pump, the oil-out of the oil inlet of the slippage pump and the hydraulic oil container
Connection, the oil-out of the slippage pump is connected with the oil inlet of the main pump group, and the oil return opening of the hydraulic oil container is changed with described
To being provided with the first check valve in the oil return opening connection of valve group and the fluid pressure line of connection, the oil inlet of first check valve with
The oil return opening connection of the commutation valve group, the oil-out of first check valve is connected with the oil return opening of the hydraulic oil container；
The commutation valve group includes three seven logical reversal valve and three position three-way change valves, the of described three seven logical reversal valves
One hydraulic fluid port and the second hydraulic fluid port are connected by the balance valve group with two hydraulic fluid ports of the hydraulic motor respectively, and described three seven lead to
3rd hydraulic fluid port of reversal valve is connected with the oil-out of the main pump group, described three 7 the 4th hydraulic fluid ports and described three of logical reversal valve
First hydraulic fluid port of position three-way diverter valve connect with control port, described three 7 the 5th hydraulic fluid ports of logical reversal valve, the 6th hydraulic fluid port and
The 3rd hydraulic fluid port connection of the three position three-way change valve, described three seven logical 7th hydraulic fluid ports of reversal valve and entering for the main pump group
Hydraulic fluid port is connected, and the second hydraulic fluid port of the three position three-way change valve is connected with the control port of the main pump group；
The main pump group includes volume adjustable hydraulic pump, the first two position three way directional control valve, the second two position three way directional control valve and the 3rd
Two position three way directional control valve, the oil-out of the volume adjustable hydraulic pump respectively with the control port of first two position three way directional control valve and
Second hydraulic fluid port, the control port of second two position three way directional control valve and the second hydraulic fluid port, the 3rd two position three way directional control valve
The connection of first hydraulic fluid port, the first hydraulic fluid port of first two position three way directional control valve and the hydraulic fluid port of the second two position three way directional control valve the 3rd
Connection, the first hydraulic fluid port of second two position three way directional control valve is connected with the 3rd hydraulic fluid port of the 3rd two position three way directional control valve,
Second hydraulic fluid port of the 3rd two position three way directional control valve and the 3rd hydraulic fluid port of first two position three way directional control valve are connected directly respectively
Motivation structure is controlling the displacement variation of the volume adjustable hydraulic pump, the control port of first two position three way directional control valve and described three
The second hydraulic fluid port connection of position three-way diverter valve.
Further, the balance valve group includes bi-bit bi-pass reversal valve, the first hydraulic fluid port of the bi-bit bi-pass reversal valve
The first hydraulic fluid port with described three seven logical reversal valves is connected, the second hydraulic fluid port and the hydraulic motor of the bi-bit bi-pass reversal valve
The connection of one of hydraulic fluid port, the second hydraulic fluid ports of the logical reversal valve of the control port of the bi-bit bi-pass reversal valve and described three seven
Connection, the second check valve and choke valve are provided with the bi-bit bi-pass reversal valve, when the bi-bit bi-pass reversal valve is in the
During one state, the second check valve conducting, and one end of the oil inlet of second check valve and described three seven logical commutations
The first hydraulic fluid port connection of valve, when the bi-bit bi-pass reversal valve is in the second state, the choke valve conducting.
Further, the oil inlet end of the bi-bit bi-pass reversal valve is parallel with an overflow valve with oil-out end.
Further, the control port of the bi-bit bi-pass reversal valve and described three 7 second oil of logical reversal valve
Choke valve and filter are provided with the oil circuit of mouth connection.
Further, the fluid pressure line that connects is between the oil return opening and the oil inlet of the main pump group of the commutation valve group
Main line, the oil inlet of first check valve is connected with the main line, oil inlet and the master of first check valve
The position of pipeline connection is the peak in the fluid pressure line of hydraulic control system.
Further, it is provided with pressure on the oil circuit between the oil return opening and the oil inlet of the main pump group of the commutation valve group
Force snesor.
Further, set on the pipeline for being connected between the oil-out of the main pump group and the oil inlet of the commutation valve group
There is the 3rd check valve.
Further, an oil return pipeline and the oil return pipeline are provided between the oil scavenge pump and the hydraulic oil container
On be provided with the 4th check valve.
The beneficial effect of technical scheme provided in an embodiment of the present invention is：
It is connected with slippage pump by by repairing motor, slippage pump is respectively communicated with hydraulic oil container and main pump group, can be in main pump
For fully supplement hydraulic oil removes the gas in hydraulic system side by side in hydraulic system before group work, due to returning in hydraulic oil container
The first check valve is provided with the fluid pressure line that hydraulic fluid port is connected with the oil return opening of commutation valve group so that hydraulic pressure is full of in fluid pressure line
First check valve can produce certain back pressure when oily, and then cause that the hydraulic oil at main pump group inlet port forms certain pressure,
Increase the suction capacity of main pump group, main pump group can be prevented to be emptied and vibrate, it is ensured that the service life of main pump group.
Brief description of the drawings
Technical scheme in order to illustrate more clearly the embodiments of the present invention, below will be to that will make needed for embodiment description
Accompanying drawing is briefly described, it should be apparent that, drawings in the following description are only some embodiments of the present invention, for
For those of ordinary skill in the art, on the premise of not paying creative work, other can also be obtained according to these accompanying drawings
Accompanying drawing.
Fig. 1 is a kind of ocean engineering crane hydraulic control system structure chart provided in an embodiment of the present invention.
Specific embodiment
To make the object, technical solutions and advantages of the present invention clearer, below in conjunction with accompanying drawing to embodiment party of the present invention
Formula is described in further detail.
Embodiment
Referring to Fig. 1, a kind of ocean engineering crane hydraulic control system, hydraulic control system are the embodiment of the invention provides
Including main motor 1, main pump group 2, commutation valve group 3, balance valve group 4, hydraulic motor 5, main motor 1 is connected with main pump group 2, main pump group
2 oil-out P1 is connected with the oil inlet P 2 of commutation valve group 3, and the first oil-out of the valve group 3 that commutates, the second oil-out pass through respectively
Balance valve group 4 connect with two hydraulic fluid ports A4, B4 of hydraulic motor 5, commutation valve group 3 oil return inlet T 1 and main pump group 2 oil inlet
S1 is connected.
Wherein, hydraulic control system also includes repairing motor 6, slippage pump 7 and hydraulic oil container 8, repairing motor 6 and slippage pump
7 connections, the oil inlet S2 of slippage pump 7 is connected with the oil-out S3 of hydraulic oil container 8, oil-out P3 and the main pump group 2 of slippage pump 7
Oil inlet S1 is connected, and is set on the fluid pressure line that the oil return inlet T 2 of hydraulic oil container 8 is connected and connected with the oil return inlet T 1 of the valve group 3 that commutates
It is equipped with the first check valve 9, the oil inlet of the first check valve 9 is connected with the oil return inlet T 1 of commutation valve group 3, the first check valve 9 goes out
Hydraulic fluid port is connected with the oil return inlet T 2 of hydraulic oil container 8.
Specifically, the hydraulic control system in the present embodiment mainly divides two parts, and Part I is main motor 1, main pump group
2nd, the main hydraulic system that commutation valve group 3, balance valve group 4 and hydraulic motor 5 are constituted, main hydraulic system drives master by main motor 1
The pumping hydraulic of pump group 2 oil, the mesh of the rotating of hydraulic motor 5 is controlled through two kinds of flow directions of the control hydraulic oil of valve group 3 that commutates to reach
, the final action for realizing each mechanism of control crane, balance valve group 4 is used for when crane is in and declines operating mode, to pipeline
In hydraulic oil form certain buffer brake so that hydraulic motor 5 at the uniform velocity slowly runs, prevent the goods stall on crane
Decline initiation accident；Part II is the repairing hydraulic system that repairing motor 6, slippage pump 7 and hydraulic oil container 8 are constituted, by mending
The control slippage pump 7 of oily motor 6 is operated, and the hydraulic oil that slippage pump 7 starts in extraction hydraulic oil container 8 is filled with the hydraulic pressure of main hydraulic system
In pipeline, the air in main hydraulic system pipeline can be discharged through hydraulic oil container 8 before the work of main pump group 2, in being pipeline
The hydraulic oil of abundance is filled into, the first check valve is arranged on the working connection (oil return of commutation valve group 3 of main hydraulic system in the present embodiment
Fluid pressure line between mouthful T1 and oil inlet S1 of main pump group 2) on the pipeline that is connected and hydraulic oil container 8 between, due to check valve
With certain Opening pressure and simple structure cost is relatively low, so using check valve as counterbalance valve, pipe in the present embodiment
Certain back pressure can be formed at the first check valve so that the hydraulic oil tool at the inlet port of main pump group 2 after hydraulic oil is supplied in road
Have certain precompression, so increase when main pump group 2 is operated from oil absorption, main pump group 2 can be prevented to be emptied and vibrate, protect
The service life of main pump group 2 is demonstrate,proved.
Further, commutation valve group 3 includes three seven logical reversal valve 3a and three position three-way change valve 3b, three seven logical commutations
First hydraulic fluid port (B1) and the second hydraulic fluid port (A1) of valve 3a are respectively by balancing two hydraulic fluid ports (B4, A4) of valve group 4 and hydraulic motor 5
Connection, the 3rd hydraulic fluid ports (P2) of three seven logical reversal valve 3a are connected with the oil-out of main pump group 2, three seven lead to reversal valve 3a the
Four hydraulic fluid ports are connected with first hydraulic fluid port of three position three-way change valve 3b and control port, three 7 the 5th hydraulic fluid ports of logical reversal valve 3a,
6th hydraulic fluid port is connected with the 3rd hydraulic fluid port of three position three-way change valve 3b, three seven the 7th hydraulic fluid ports and main pump group 2 for leading to reversal valve 3a
Oil inlet connection, the second hydraulic fluid port Ls2 of three position three-way change valve 3b connects with the control port Ls1 of main pump group 2.
Specifically, it with hydraulic valve piece icon lower right corner hydraulic fluid port is that the hydraulic fluid port naming rule of hydraulic valve piece is in the present embodiment
One hydraulic fluid port, names other hydraulic fluid ports successively clockwise, when three seven logical reversal valve 3a are in first state, three seven logical reversal valve 3a
The first hydraulic fluid port, the second hydraulic fluid port connected with the 4th hydraulic fluid port, the 5th hydraulic fluid port, the 7th hydraulic fluid port respectively, while the 3rd hydraulic fluid port, the 6th hydraulic fluid port
It is not turned on, now main hydraulic system does not work for original state；When three seven logical reversal valve 3a are in the second state, three seven lead to
First hydraulic fluid port of reversal valve 3a and the 7th hydraulic fluid port are connected, and the second hydraulic fluid port and the 5th hydraulic fluid port are connected, and the 3rd hydraulic fluid port and the 4th hydraulic fluid port connect
Logical, the 6th hydraulic fluid port is not turned on, and the hydraulic oil traffic organising hydraulic motor 5 of the valve group 3 that now commutates guiding is inverted；Three seven logical commutations
When valve 3a is in the third state, three 7 first hydraulic fluid ports and the connection of the 6th hydraulic fluid port, the second hydraulic fluid port and the 7th oil of logical reversal valve 3a
Mouth connection, the 3rd hydraulic fluid port and the 4th hydraulic fluid port are connected, and the 5th hydraulic fluid port is not turned on, and the hydraulic oil of the valve group 3 that now commutates guiding flows to control
Hydraulic motor processed 5 is rotated forward.
When three position three-way change valve 3b is in initial first state, three hydraulic fluid ports of three position three-way change valve 3b are not led
Logical, hydraulic oil can not flow in pipeline；With the entrance of hydraulic oil, when three position three-way change valve 3b is in first state, three
First hydraulic fluid port of three-way diverter valve 3b and the 3rd hydraulic fluid port are connected, and the second hydraulic fluid port is not turned on, and the hydraulic oil in pipeline smoothly circulates；When
Valve core opening in commutation valve group 3 is excessive, and three position three-way change valve 3b switchs to the third state when causing hydraulic fluid flow rate excessive, the
One hydraulic fluid port is connected with the second hydraulic fluid port, the 3rd hydraulic fluid port respectively, and section hydraulic oil flows back to main pump group 2 and controls the discharge capacity of main pump group 2, from
And control main pump group 2 export hydraulic oil uninterrupted, adjust hydraulic motor 5 rotating speed.
Further, main pump group 2 includes that volume adjustable hydraulic pump 2a, the first two position three way directional control valve 2b, the second two-position three way are changed
To valve 2c and the 3rd two position three way directional control valve 2d, the oil-out of volume adjustable hydraulic pump 2a is respectively with the first two position three way directional control valve 2b's
Control port and the second hydraulic fluid port, the control port of the second two position three way directional control valve 2c and the second hydraulic fluid port, the commutation of the 3rd two-position three way
The first hydraulic fluid port connection of valve 2d, first hydraulic fluid port and the oil of the second two position three way directional control valve 2c the 3rd of the first two position three way directional control valve 2b
Mouth connection, first hydraulic fluid port of the second two position three way directional control valve 2c is connected with the 3rd hydraulic fluid port of the 3rd two position three way directional control valve 2d, the
3rd hydraulic fluid port of second hydraulic fluid port of three two position three way directional control valve 2d and the first two position three way directional control valve 2b connects straight-moving mechanism respectively
With the displacement variation of control variables hydraulic pump 2a, control port and the three position three-way change valve 3b of the first two position three way directional control valve 2b
The second hydraulic fluid port connection.
Specifically, volume adjustable hydraulic pump 2a is used to that kinetic energy to be switched into hydraulic energy, the first two-position three way under the drive of main motor 1
Reversal valve 2b and the second two position three way directional control valve 2c are identical, are all that the first hydraulic fluid port and the 3rd hydraulic fluid port are connected in the first state, the
Two hydraulic fluid ports are not turned on, and the first hydraulic fluid port is not turned under the second state, and the second hydraulic fluid port and the 3rd hydraulic fluid port are connected；3rd two-position three way commutates
The first hydraulic fluid port is not turned on valve 2d in the first state, and the second hydraulic fluid port and the 3rd hydraulic fluid port are turned on, the first hydraulic fluid port and the under the second state
Three hydraulic fluid ports are connected, and the second hydraulic fluid port is not turned on；Three two position three way directional control valves are all the hydraulic oil and reversal valve exported in main pump group 2
Under the control of the hydraulic oil of the feedback of group 3, straight-moving mechanism is driven to move back and forth to adjust the displacement size of main pump group 2, it is final to realize
Control to the rotating speed of hydraulic motor 5.
Further, balance valve group 4 includes bi-bit bi-pass reversal valve 4a, first hydraulic fluid port and three of bi-bit bi-pass reversal valve 4a
The first hydraulic fluid ports connection of the logical reversal valve 3a in position seven, second hydraulic fluid port of bi-bit bi-pass reversal valve 4a and hydraulic motor 5 one of them
Hydraulic fluid port is connected, and second hydraulic fluid port of the control port of bi-bit bi-pass reversal valve 4a reversal valve 3a logical with three seven is connected.Bi-bit bi-pass
The second check valve and choke valve are provided with reversal valve 4a, when bi-bit bi-pass reversal valve 4a is in first state, second is unidirectional
Valve is turned on, and first hydraulic fluid port of one end of the oil inlet of the second check valve reversal valve 3a logical with three seven is connected, and works as bi-bit bi-pass
When reversal valve 4a is in the second state, choke valve conducting.
Specifically, balance valve group 4 has four hydraulic fluid ports A2, A3, B2, B3, and wherein A2, B2 leads to reversal valves with three seven respectively
3 the second hydraulic fluid port A1, the first hydraulic fluid port B1 connection, A3, B3 are connected with hydraulic fluid port A4, B4 of hydraulic motor 5 respectively, when commutation valve group 3
During the direction that the flow direction of the hydraulic oil for controlling is rotated forward for hydraulic motor 5, bi-bit bi-pass reversal valve 4a is in first state, now rises
Heavy-duty machine is in and rises operating mode；When the direction that the flow direction of the hydraulic oil that the valve group 3 that commutates is controlled is inverted for hydraulic motor 5, two two
The second state can be changed at logical reversal valve 4a after pilot control, crane is in and declines operating mode, now bi-bit bi-pass commutation
Choke valve in valve 4a can reduce the flow of hydraulic oil, reduce the rotating speed of hydraulic motor 5 to prevent goods stall from declining and cause thing
Therefore.
Further, the oil inlet end of bi-bit bi-pass reversal valve 4a is parallel with an overflow valve 4b with oil-out end.
Specifically, overflow valve 4b is used for when crane is in and declines the reversion of operating mode hydraulic motor 5, auxiliary limitation hydraulic oil
Flow velocity, the pressure opposite with the reversion of hydraulic motor 5 is produced in fluid pressure line, the oil pressure in stable hydraulic pipeline is reaching
Prevent the situation that goods stall declines on crane.
Further, second hydraulic fluid port of the control port of bi-bit bi-pass reversal valve 4a reversal valve 3a logical with three seven is connected
Choke valve and filter are provided with oil circuit.
Specifically, balance valve group 4 is accurate hydraulic valve bank, and current limliting is carried out and using filter to pipeline using choke valve
In hydraulic oil filtered, safely worked with the valve such as the bi-bit bi-pass reversal valve 4a stabilization ensured in balance valve group 4.
Further, the fluid pressure line for being connected between the oil return opening and the oil inlet of main pump group 2 of commutation valve group 3 is supervisor
Road, the oil inlet of the first check valve 9 is connected with main line, and the position T4 that the oil inlet of the first check valve 9 is connected with main line is
Peak in the fluid pressure line of hydraulic control system.
Specifically, the hydraulic control system in the present embodiment chooses entering for the first check valve 9 during actual installation
The position T4 points that hydraulic fluid port is connected with main line can so cause repairing as the peak on whole hydraulic system locus
After abundant repairing, unnecessary hydraulic oil returns to hydraulic oil container 8 to pump 7 through peak T4 from the first check valve 9, is easy to main hydraulic pressure
Air in the fluid pressure line of system is fully discharged.
Further, it is provided with pressure sensing on the oil circuit between the oil return opening and the oil inlet of main pump group 2 of commutation valve group 3
Device 10.
Specifically, pressure sensor 10 is arranged on the main fluid pressure line connected between commutation valve group 3 and main pump group 2, can
With the oil pressure of hydraulic oil in the main fluid pressure line of real-time detection, in the pipeline for judging hydraulic control system hydraulic oil whether full of carrying
For foundation.
Further, the 3rd is provided with the pipeline for being connected between the oil-out of main pump group 2 and the oil inlet of commutation valve group 3
Check valve 11.
Specifically, the 3rd check valve 11 is arranged at the oil-out of main pump group 2, mainly to the hydraulic oil in pipeline
Play non-return, can prevent the oil pressure of hydraulic system from raising the hydraulic pressure for causing pressure oil reverse back and damaging in main pump group 2 suddenly
Pump 2a.
Further, it is provided between oil scavenge pump and hydraulic oil container 8 on one article of oil return pipeline and oil return pipeline and is provided with
Four check valves 12.
Specifically, after the hydraulic oil for filling into abundance during slippage pump 7 is hydraulic system, when slippage pump 7 continues repairing, the 4th
Check valve 12 can be returned directly to hydraulic oil container 8 with the unnecessary hydraulic oil of leader.
The operating process of the crane hydraulic control system that the present embodiment is provided is as follows：
It is again started up when starting for the first time after crane changes hydraulic oil during maintaining or after crane shutdown
When, first starting repairing motor 6, repairing motor 6 drives slippage pump 7 toward delivery hydraulic pressure oil in main hydraulic system, while excluding main liquid
Gas in the pipeline of pressure system, when hydraulic oil is full of gradually in main hydraulic system, unnecessary hydraulic oil is through the first check valve 9
Fuel tank is flowed back to the 4th check valve 12, when the oil pressure that pressure sensor detects hydraulic oil in main line reaches setting value, is said
Hydraulic oil has been completely filled with bright pipeline, could now start the main motor 1 in main hydraulic system, and main hydraulic system brings into operation
Drive crane work.
A kind of ocean engineering crane hydraulic control system provided in an embodiment of the present invention, by by repairing motor and repairing
Pump is connected, and slippage pump is respectively communicated with hydraulic oil container and main pump group, is fully mended in being hydraulic system before the work of main pump group
Topping up is pressed oil and excludes the gas in hydraulic system, is connected with the oil return opening of commutation valve group due to the oil return opening in hydraulic oil container
The first check valve is provided with fluid pressure line so that the first check valve can produce certain back of the body when hydraulic oil is full of in fluid pressure line
Pressure, and then cause that the hydraulic oil at main pump group inlet port forms certain malleation, increasing the suction capacity of main pump group, can prevent
Main pump group is emptied and vibrates, it is ensured that the service life of main pump group.
The foregoing is only presently preferred embodiments of the present invention, be not intended to limit the invention, it is all it is of the invention spirit and
Within principle, any modification, equivalent substitution and improvements made etc. should be included within the scope of the present invention.
Claims (8)
1. a kind of ocean engineering crane hydraulic control system, the hydraulic control system includes main motor, main pump group, reversal valve
Group, balance valve group, hydraulic motor, the main motor are connected with the main pump group, oil-out and the commutation of the main pump group
The oil inlet connection of valve group, the first oil-out, second oil-out of the commutation valve group are respectively by balance valve group and the institute
Two hydraulic fluid ports connection of hydraulic motor is stated, the oil return opening of the commutation valve group is connected with the oil inlet of the main pump group, its feature
It is that the hydraulic control system also includes repairing motor, slippage pump and hydraulic oil container,
The repairing motor is connected with the slippage pump, and the oil inlet of the slippage pump connects with the oil-out of the hydraulic oil container
Logical, the oil-out of the slippage pump is connected with the oil inlet of the main pump group, the oil return opening of the hydraulic oil container and the commutation
The first check valve, the oil inlet of first check valve and institute are provided with the oil return opening connection of valve group and the fluid pressure line of connection
The oil return opening connection of commutation valve group is stated, the oil-out of first check valve is connected with the oil return opening of the hydraulic oil container；
The commutation valve group includes three seven logical reversal valve and three position three-way change valves, described three 7 first oil of logical reversal valve
Mouth and the second hydraulic fluid port are connected by the balance valve group with two hydraulic fluid ports of the hydraulic motor respectively, described three seven logical commutations
3rd hydraulic fluid port of valve is connected with the oil-out of the main pump group, described three 7 the 4th hydraulic fluid ports of logical reversal valve with described three three
First hydraulic fluid port of logical reversal valve connect with control port, described three seven lead to the 5th hydraulic fluid port of reversal valve, the 6th hydraulic fluid port with it is described
The 3rd hydraulic fluid port connection of three position three-way change valve, the oil inlet of described three 7 the 7th hydraulic fluid ports of logical reversal valve and the main pump group
Connection, the second hydraulic fluid port of the three position three-way change valve is connected with the control port of the main pump group；
The main pump group includes volume adjustable hydraulic pump, the first two position three way directional control valve, the second two position three way directional control valve and the three or two
Three-way diverter valve, the oil-out of the volume adjustable hydraulic pump respectively with the control port and second of first two position three way directional control valve
Hydraulic fluid port, the control port of second two position three way directional control valve and the second hydraulic fluid port, the first of the 3rd two position three way directional control valve
Hydraulic fluid port is connected, and the first hydraulic fluid port of first two position three way directional control valve connects with the hydraulic fluid port of the second two position three way directional control valve the 3rd
Logical, the first hydraulic fluid port of second two position three way directional control valve is connected with the 3rd hydraulic fluid port of the 3rd two position three way directional control valve, institute
3rd hydraulic fluid port of the second hydraulic fluid port and first two position three way directional control valve of stating the 3rd two position three way directional control valve connects direct acting respectively
Mechanism to control the displacement variation of the volume adjustable hydraulic pump, the control port of first two position three way directional control valve with described three
The second hydraulic fluid port connection of three-way diverter valve.
2. hydraulic control system according to claim 1, it is characterised in that the balance valve group is changed including bi-bit bi-pass
To valve, the first hydraulic fluid port of the bi-bit bi-pass reversal valve is connected with the first hydraulic fluid port of described three seven logical reversal valves, described two
Second hydraulic fluid port of two way selected valve is connected with one of hydraulic fluid port of the hydraulic motor, the control of the bi-bit bi-pass reversal valve
Hydraulic fluid port connect with the second hydraulic fluid ports of described three seven logical reversal valves, be provided with the bi-bit bi-pass reversal valve the second check valve with
Choke valve, when the bi-bit bi-pass reversal valve is in first state, the second check valve conducting, and second check valve
One end of oil inlet connect with the first hydraulic fluid ports of described three seven logical reversal valves, when the bi-bit bi-pass reversal valve is in second
During state, the choke valve conducting.
3. hydraulic control system according to claim 2, it is characterised in that the oil inlet end of the bi-bit bi-pass reversal valve
An overflow valve is parallel with oil-out end.
4. hydraulic control system according to claim 2, it is characterised in that the control port of the bi-bit bi-pass reversal valve
Choke valve and filter are provided with the oil circuit connected with the second hydraulic fluid port of described three seven logical reversal valves.
5. hydraulic control system according to claim 1, it is characterised in that the oil return opening of the commutation valve group and the master
The fluid pressure line connected between the oil inlet of pump group is main line, and oil inlet and the main line of first check valve connect
It is logical, the position that the oil inlet of first check valve connect with the main line be hydraulic control system fluid pressure line in most
High point.
6. hydraulic control system according to claim 1, it is characterised in that the oil return opening of the commutation valve group and the master
Pressure sensor is provided with oil circuit between the oil inlet of pump group.
7. hydraulic control system according to claim 1, it is characterised in that the oil-out of the main pump group and the commutation
The 3rd check valve is provided with the pipeline connected between the oil inlet of valve group.
8. hydraulic control system according to claim 1, it is characterised in that between the slippage pump and the hydraulic oil container
It is provided with one article of oil return pipeline and the oil return pipeline and is provided with the 4th check valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410627473.4A CN104358722B (en) | 2014-11-10 | 2014-11-10 | A kind of ocean engineering crane hydraulic control system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410627473.4A CN104358722B (en) | 2014-11-10 | 2014-11-10 | A kind of ocean engineering crane hydraulic control system |
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| Publication Number | Publication Date |
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| CN104358722A CN104358722A (en) | 2015-02-18 |
| CN104358722B true CN104358722B (en) | 2017-06-20 |
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| CN201410627473.4A Active CN104358722B (en) | 2014-11-10 | 2014-11-10 | A kind of ocean engineering crane hydraulic control system |
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| CN107117534B (en) * | 2017-03-28 | 2018-12-14 | 武汉船用机械有限责任公司 | A kind of hydraulic control system of crane |
| CN107585696B (en) * | 2017-07-31 | 2019-10-08 | 武汉船用机械有限责任公司 | A kind of hydraulic system of winch |
| CN110848181B (en) * | 2019-10-18 | 2021-04-23 | 中联重科股份有限公司 | Hydraulic transmission system and crane |
| CN112879391B (en) * | 2021-02-20 | 2023-04-18 | 潍柴动力股份有限公司 | Oil supplementing device and closed system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP4632583B2 (en) * | 2001-07-10 | 2011-02-16 | 住友建機株式会社 | Electric closed circuit hydraulic cylinder drive |
| US7444809B2 (en) * | 2006-01-30 | 2008-11-04 | Caterpillar Inc. | Hydraulic regeneration system |
| CN201771496U (en) * | 2010-09-03 | 2011-03-23 | 安徽理工大学 | Hydraulic tracting system for shearer driven by load sensitive pump |
| CN102425576B (en) * | 2011-11-21 | 2015-04-22 | 武汉船用机械有限责任公司 | Motor system having passive cable laying function |
| CN202746339U (en) * | 2012-09-11 | 2013-02-20 | 中联重科股份有限公司 | Hydraulic filtering system, hydraulic control system comprising same and engineering machinery |
| CN202924661U (en) * | 2012-12-03 | 2013-05-08 | 中联重科股份有限公司 | Hydraulic system of hoisting mechanism and crane |
| CN103277353B (en) * | 2013-05-08 | 2015-06-10 | 燕山大学 | Unmanned aerial vehicle low impact catapult pneumatic and hydraulic system |
| CN103541937A (en) * | 2013-10-29 | 2014-01-29 | 中国船舶重工集团公司第七�三研究所 | Hydraulic enclosed loading system |
| CN103615420B (en) * | 2013-11-28 | 2016-03-16 | 中国船舶重工集团公司第七0四研究所 | A kind of compact type steering wheel special valve group |
| CN104019066B (en) * | 2014-05-30 | 2015-12-30 | 武汉船用机械有限责任公司 | A kind of ocean platform lifting mechanism hydraulic control system |
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