CN104925685B - A kind of winch hydraulic system that cable is led by stepless time adjustment constant tensile control - Google Patents
A kind of winch hydraulic system that cable is led by stepless time adjustment constant tensile control Download PDFInfo
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- CN104925685B CN104925685B CN201510372268.2A CN201510372268A CN104925685B CN 104925685 B CN104925685 B CN 104925685B CN 201510372268 A CN201510372268 A CN 201510372268A CN 104925685 B CN104925685 B CN 104925685B
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/02—Driving gear
- B66D1/08—Driving gear incorporating fluid motors
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/28—Other constructional details
- B66D1/40—Control devices
- B66D1/42—Control devices non-automatic
- B66D1/44—Control devices non-automatic pneumatic of hydraulic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a kind of winch hydraulic system that cable is led by stepless time adjustment constant tensile control, it is related to tension force winch hydraulic system field.The system includes fuel tank, motor, variable delivery hydraulic pump group, check valve, high-pressure overflow valve, backpressure overflow valve, motor operation valve group, winch motor, brake oil cylinder, board-like overflow valve, proportional pressure control valve, the first screw thread inserting type shuttle valve, the second screw thread inserting type shuttle valve, bi-bit bi-pass normally-closed ball valve and two-position three-way electromagnetic ball valve.The present invention can not only realize leading the stepless time adjustment and constant tensile control requirement of cable winch, and can solve the problem that the problem for causing power loss in conventional hydraulic winch constant tension control system due to high pressure kicks, and then energy saving, improve the efficiency of hydraulic system.The present invention can not only reduce the volumetric spaces of system occupancy using the design of integrated form valve block, and can reduce system pipeline quantity, reduce fault rate, be easy for installation and maintenance, and can realize mass and standardized production.
Description
Technical field
The present invention relates to tension force winch hydraulic system field, and in particular to one kind passes through stepless time adjustment constant tensile control
Lead the winch hydraulic system of cable.
Background technology
Equipment is hung in marine environment complicated and changeable, can be received because of external cause (such as the influence of heaving of the sea and ocean current etc.)
To extra additional forces, and then cause that hanging equipment drifts with the tide, and hangs the less stable of equipment, more likely damage
Or lose.
In order to ensure the stability of equipment, hanging device hangs precision equipment and (for example carries the equipment or water of precision instrument
Lower manned submersible) when, it usually needs assist to hang using cable ballast is led.Precision equipment is led on cable hawser during hanging
Tension force need to keep constant, and then make to lead cable hawser and be in tensioning state.
But, due to the influence such as wave or ocean current in marine environment, lead cable hawser and be likely to occur loose or tension
Phenomenon；If hawser is excessively loose, can make to lead that cable ballast is ineffective, precision equipment cannot normally hang and reclaim, or even damage；If cable
Rope tension, may break and lead cable, and in turn resulting in precision equipment cannot hang and reclaim, in some instances it may even be possible to cause device losses.
The content of the invention
For defect present in prior art, stepless time adjustment identical tension control is passed through it is an object of the invention to provide one kind
Guide the winch hydraulic system of cable.The present invention can not only realize leading the stepless time adjustment and constant tensile control requirement of cable winch, and
And can solve the problem that the problem for causing power loss in conventional hydraulic winch constant tension control system due to high pressure kicks, Jin Erjie
About the energy, significantly improves the efficiency of hydraulic system.At the same time, the present invention can not only be reduced using the design of integrated form valve block
The volumetric spaces that system takes, and system pipeline quantity can be substantially reduced, fault rate is reduced, it is easy for installation and maintenance, energy
Enough realize mass and standardized production.
To achieve the above objectives, the winch hydraulic system that cable is led by stepless time adjustment constant tensile control that the present invention is provided,
Including fuel tank, motor, variable delivery hydraulic pump group, check valve, high-pressure overflow valve, backpressure overflow valve, motor operation valve group, winch horse
Up to, brake oil cylinder, board-like overflow valve, proportional pressure control valve, the first screw thread inserting type shuttle valve, the second screw thread inserting type shuttle valve, two
Two-way normally-closed ball valve and two-position three-way electromagnetic ball valve；
The motor operation valve group includes pressure-reducing valve, the first solenoid-operated proportional pressure-reducing valve, the second solenoid-operated proportional pressure-reducing valve, two-way
Recuperation valve, fixed restriction plug, choke valve, liquid controlled reversing main valve, brake unclasp valve, low pressure relief valve, shuttle valve, balanced valve, section
Stream valve, guide's pilot relief valve, Fill valve and one-way throttle valve；
P mouthfuls of the entrance of the pressure-reducing valve and motor operation valve group is communicated, the outlet of pressure-reducing valve respectively with the first electromagnetism ratio
Example pressure-reducing valve, the entrance of the second solenoid-operated proportional pressure-reducing valve are communicated, outlet and the liquid controlled reversing main valve of the first solenoid-operated proportional pressure-reducing valve
Left position liquid controling cavity communicate, the outlet of the second solenoid-operated proportional pressure-reducing valve is communicated with the right position liquid controling cavity of liquid controlled reversing main valve；
The leakage hydraulic fluid port of pressure-reducing valve leakage hydraulic fluid port respectively with the first solenoid-operated proportional pressure-reducing valve, the second solenoid-operated proportional subtract
The leakage hydraulic fluid port of pressure valve is communicated；Leakage oil circuit of the leakage hydraulic fluid port of pressure-reducing valve also with motor operation valve group is communicated, motor operation valve
The leakage oil circuit of group operates the leakage hydraulic fluid port D of valve group to be communicated with fuel tank by motor；
The entrance of the two-way recuperation valve is communicated with P mouthfuls of motor operation valve group, and outlet and the hydraulic control of two-way recuperation valve are changed
Communicated to P mouthfuls of main valve；The entrance of fixed restriction plug is communicated with the entrance of two-way recuperation valve, outlet and the throttling of fixed restriction plug
The entrance of valve, the entrance of low pressure relief valve are interconnected；The spring cavity control mouth for exporting respectively with two-way recuperation valve of choke valve,
P2 mouthfuls of first screw thread inserting type shuttle valve is communicated；
T mouthfuls of the liquid controlled reversing main valve is communicated with T mouthfuls of motor operation valve group, A mouthfuls and balance of liquid controlled reversing main valve
The entrance of valve is communicated, and the outlet of balanced valve is communicated with A mouthfuls of motor operation valve group；B mouthfuls and motor of the liquid controlled reversing main valve
B mouthfuls of operation valve group is communicated；
The entrance of guide's pilot relief valve is communicated with the outlet of balanced valve, the outlet of guide's pilot relief valve respectively with
Motor operation T mouthful of valve group, the entrance of Fill valve are communicated, and the outlet of Fill valve and motor operate B mouthfuls of valve group to communicate；
P1 mouthfuls of the shuttle valve is connected with A mouthfuls of liquid controlled reversing main valve, and P2 mouthfuls of shuttle valve with B mouthfuls of liquid controlled reversing main valve even
Connect；The outlet respectively with low pressure relief valve of A mouthfuls of shuttle valve, P1 mouthfuls of the second screw thread inserting type shuttle valve be connected；
Described choke valve one end is communicated with the hydraulic control mouthful of balanced valve, and the other end is communicated with B mouthfuls of liquid controlled reversing main valve；Braking
Device unclasps valve and is linked with liquid controlled reversing main valve, and brake unclasps A mouthfuls of valve and motor operates the leakage hydraulic fluid port D of valve group to communicate, and makes
Dynamic device unclasp valve B mouthfuls is communicated with the outlet of pressure-reducing valve, and brake unclasps P mouthfuls of valve and is connected with the throttling end of one-way throttle valve,
S hydraulic fluid port of the one-way throttle valve also with motor operation valve group is communicated；
The hydraulic control of guide's pilot relief valve mouthful be connected with the entrance of board-like overflow valve, the outlet of board-like overflow valve and the
P1 mouthfuls of connection of one screw thread inserting type shuttle valve；A mouthfuls of first screw thread inserting type shuttle valve connects with A mouthfuls of bi-bit bi-pass normally-closed ball valve
Connect, B mouthfuls of bi-bit bi-pass normally-closed ball valve is connected with the entrance of proportional pressure control valve, the outlet of proportional pressure control valve respectively with winch motor
Drain tap, motor operation valve group leakage hydraulic fluid port D and fuel tank communicate；
P mouthfuls of the two-position three-way electromagnetic ball valve communicates with P2 mouthfuls of the second screw thread inserting type shuttle valve, the second thread cartridge
A mouthfuls of formula shuttle valve is communicated with K mouthfuls of the load feedback mouthful of variable delivery hydraulic pump group；A mouthfuls of two-position three-way electromagnetic ball valve is operated with motor
The leakage hydraulic fluid port D of valve group is communicated；B mouthfuls of two-position three-way electromagnetic ball valve is communicated with the oil inlet P mouthful of motor operation valve group.
On the basis of above-mentioned technical proposal, the motor is connected with variable delivery hydraulic pump group, variable delivery hydraulic pump group it is fuel-displaced
Mouthful P entrance respectively with check valve, the entrance of high-pressure overflow valve are connected, the outlet of check valve and the oil inlet of motor operation valve group
P is connected；The oil return inlet T of motor operation valve group is connected by backpressure overflow valve after being connected with the outlet of high-pressure overflow valve with fuel tank.
On the basis of above-mentioned technical proposal, the oil inlet of the winch motor is connected with A mouthfuls of motor operation valve group, twists
The oil return opening that vehicle and horse reach is connected with B mouthfuls of motor operation valve group, and rod chamber and the S hydraulic fluid ports of motor operation valve group of brake oil cylinder connect
Connect.
On the basis of above-mentioned technical proposal, the variable delivery hydraulic pump group include shaft orientation plunger variable pump, variable delivery hydraulic cylinder,
Constant power control valve, load-sensitive valve, overflow valve, first throttle plug and the second orifice plug；
The inlet port of the shaft orientation plunger variable pump is communicated with fuel tank, the oil-out of shaft orientation plunger variable pump respectively with variable
P mouthfuls of hydraulic pressure pump group, the rod chamber of variable delivery hydraulic cylinder communicates；The piston rod of variable delivery hydraulic cylinder respectively with shaft orientation plunger variable pump
Variable swash plate, the spring of constant power control valve are connected；
The rod chamber of the variable delivery hydraulic cylinder respectively with load-sensitive valve A mouthfuls, load-sensitive valve are communicated without spring cavity；
Outlet of B mouthfuls of load-sensitive valve respectively with the entrance, constant power control valve of first throttle plug is communicated, P mouthfuls of load-sensitive valve
Outlet respectively with first throttle plug, the rodless cavity of variable delivery hydraulic cylinder are communicated；
The unloading port for exporting respectively with shaft orientation plunger variable pump of the constant power control valve, fuel tank are communicated；Invariable power control
The outlet respectively with the second orifice plug of the entrance of valve processed, the spring cavity of load-sensitive valve, the entrance of overflow valve are communicated；Overflow valve
Outlet is communicated with the outlet of constant power control valve, K mouthfuls of phase of the entrance of the second orifice plug and the load feedback of variable delivery hydraulic pump group mouthful
It is logical.
Compared with prior art, the advantage of the invention is that：
(1) present invention is using solenoid-operated proportional pressure-reducing valve control liquid controlled reversing main valve, with realize winch motor lifting and under
Put, can be with stepless time adjustment being lifted and being transferred；At the same time, liquid controlled reversing main valve has hand behaviour's function, and operating personnel can
In case of emergency winch motor can be operated manually.
The present invention uses load sensing control technique, and the speed of service of winch motor is not influenceed by load change, only with
The work angle of electric ratio handle is relevant.
Variable delivery hydraulic pump group of the invention has power limitation control variant patterns, when the output pressure of Variable plunger pump exceedes
During the power limitation control starting point of setting, its output flow drops under the restriction of power limitation control curve with the rising of pressure
It is low, and then cause that the speed of service of winch motor can be reduced with the increase of load.
Constant tensile control of the invention is opened by bi-bit bi-pass normally-closed ball valve, and constant tensile control value is carried out by proportional pressure control valve
Setting.
In sum, compared with the situation that hawser in the prior art was likely to occur pine or tension, the present invention is using negative
Sensitive control technology is carried, in constant tensile control pattern, in the case where output pressure is set, its discharge capacity can be certainly for variable delivery hydraulic pump group for system
Dynamic regulation, the tension force on cable hawser remains constant, and output flow is only used to maintain system to control oil and system leak, shows
The power attenuation of reduction system is write, the efficiency of system is improved.
(2) motor operation valve group of the invention is the design of integrated form valve block, its constant tensile control module and load feedback
Module is the design of integrated form valve block, can not only reduce the volumetric spaces of system occupancy, and substantially reduces system pipes way
Amount, reduces fault rate, is easy for installation and maintenance, and can realize mass and standardized production.
Brief description of the drawings
Fig. 1 be the embodiment of the present invention in led by stepless time adjustment constant tensile control cable winch hydraulic system operation principle
Figure.
In figure：1- fuel tanks, 2- motors, 3- variable delivery hydraulic pump groups, 4- check valves, 5- high-pressure overflow valves, 6- backpressure overflow valves,
7- motors operate valve group, 8- winch motors, 9- brake oil cylinders, the board-like overflow valves of 10-, 11- proportional pressure control valves, the screw threads of 12- first
Plug-in shuttle valve, 13- bi-bit bi-pass normally-closed ball valves, the screw thread inserting type shuttle valves of 14- second, 15- two-position three-way electromagnetic ball valves；
3.1- shaft orientation plunger variable pumps, 3.2- variable delivery hydraulic cylinders, 3.3- constant power control valves, 3.4- load-sensitive valves,
3.5- overflow valves, 3.6- first throttle plugs, the orifice plugs of 3.7- second；
7.1- pressure-reducing valves, the first solenoid-operated proportionals of 7.2- pressure-reducing valve, the second solenoid-operated proportionals of 7.3- pressure-reducing valve, the compensation of 7.4- two-ways
Valve, 7.5- fixed restriction plugs, 7.6- choke valves, 7.7- liquid controlled reversing main valves, 7.8- brakes unclasp valve, 7.9- low pressure spills
Valve, 7.10- shuttle valves, 7.11- balanced valves, 7.12- choke valves, 7.13- guide's pilot relief valve, 7.14- Fill valves, 7.15- is mono-
To choke valve.
Specific embodiment
The present invention is described in further detail below in conjunction with drawings and Examples.
It is shown in Figure 1, the winch hydraulic system that cable is led by stepless time adjustment constant tensile control in the embodiment of the present invention,
Including fuel tank 1, motor 2, variable delivery hydraulic pump group 3, check valve 4, high-pressure overflow valve 5, backpressure overflow valve 6, motor operation valve group 7,
Winch motor 8, brake oil cylinder 9, board-like overflow valve 10, proportional pressure control valve 11, the first screw thread inserting type shuttle valve 12, the second screw thread are inserted
Dress formula shuttle valve 14, bi-bit bi-pass normally-closed ball valve 13 and two-position three-way electromagnetic ball valve 15.
The motor operation control winch of valve group 7 hangs operation, including pressure-reducing valve 7.1, the first solenoid-operated proportional pressure-reducing valve 7.2, the
Two solenoid-operated proportional pressure-reducing valves 7.3, two-way recuperation valve 7.4, fixed restriction plug 7.5, choke valve 7.6, liquid controlled reversing main valve 7.7, system
Dynamic device unclasps valve 7.8, low pressure relief valve 7.9, shuttle valve 7.10, balanced valve 7.11, choke valve 7.12, guide's pilot relief valve
7.13rd, Fill valve 7.14 and one-way throttle valve 7.15.
Motor 2 is connected with variable delivery hydraulic pump group 3, the oil-out P of variable delivery hydraulic pump group 3 entrance, height respectively with check valve 4
The entrance of pressurized overflow valve 5 is connected, and the outlet of check valve 4 is connected with the oil inlet P of motor operation valve group 7；Motor operation valve group 7
Oil return inlet T is connected by backpressure overflow valve 6 after being connected with the outlet of high-pressure overflow valve 5 with fuel tank 1.
The oil inlet of winch motor 8 is connected with A mouthfuls of motor operation valve group 7, and oil return opening and the motor of winch motor 8 are operated
B mouthfuls of valve group 7 is connected, and the rod chamber of brake oil cylinder 9 is connected with the S hydraulic fluid ports of motor operation valve group 7.
P mouthfuls of oil circuit of the entrance of pressure-reducing valve 7.1 and motor operation valve group 7 is communicated, and the outlet of pressure-reducing valve 7.1 is respectively with first
Solenoid-operated proportional pressure-reducing valve 7.2, the entrance of the second solenoid-operated proportional pressure-reducing valve 7.3 are communicated, the outlet of the first solenoid-operated proportional pressure-reducing valve 7.2
Communicated with the left position liquid controling cavity of liquid controlled reversing main valve 7.7, outlet and the liquid controlled reversing main valve of the second solenoid-operated proportional pressure-reducing valve 7.3
7.7 right position liquid controling cavity is communicated.
The leakage hydraulic fluid port of pressure-reducing valve 7.1 leakage hydraulic fluid port, the second solenoid-operated proportional respectively with the first solenoid-operated proportional pressure-reducing valve 7.2
The leakage hydraulic fluid port of pressure-reducing valve 7.3 is communicated；Leakage oil circuit of the leakage hydraulic fluid port of pressure-reducing valve 7.1 also with motor operation valve group 7 is communicated, horse
Leakage oil circuit up to operation valve group 7 operates the leakage hydraulic fluid port D of valve group 7 to be communicated with fuel tank 1 by motor.
The entrance of two-way recuperation valve 7.4 is communicated with P mouthfuls of motor operation valve group, the outlet and hydraulic control of two-way recuperation valve 7.4
P mouthfuls of commutation main valve 7.7 is communicated；The entrance of fixed restriction plug 7.5 is communicated with the entrance of two-way recuperation valve 7.4, fixed restriction plug
7.5 outlet is interconnected with the entrance of the entrance of choke valve 7.6, low pressure relief valve 7.9；The outlet of choke valve 7.6 respectively with
The spring cavity control mouth of two-way recuperation valve 7.4, P2 mouthfuls of the first screw thread inserting type shuttle valve 12 communicate.
T mouthful of T mouthfuls of liquid controlled reversing main valve 7.7 and motor operation valve group 7 is communicated, A mouthfuls of liquid controlled reversing main valve 7.7 with put down
The entrance of weighing apparatus valve 7.11 is communicated, and the outlet of balanced valve 7.11 and motor operate A mouthfuls of valve group 7 to communicate.Liquid controlled reversing main valve 7.7
B mouthfuls communicates with B mouthfuls of motor operation valve group 7.
The entrance of guide's pilot relief valve 7.13 is communicated with the outlet of balanced valve 7.11, and guide's pilot relief valve 7.13 goes out
Entrance of the mouth respectively with motor operation T mouthful of valve group 7, Fill valve 7.14 is communicated, the outlet of Fill valve 7.14 and motor operation valve
B mouthfuls of group 7 is communicated.
P1 mouthfuls of shuttle valve 7.10 is connected with A mouthfuls of liquid controlled reversing main valve 7.7, P2 mouthfuls and liquid controlled reversing main valve of shuttle valve 7.10
7.7 B mouthfuls of connection.Outlet, the P1 of the second screw thread inserting type shuttle valve 14 respectively with low pressure relief valve 7.9 of A mouthfuls of shuttle valve 7.10
Mouth connection.
The hydraulic control mouthful of the one end of choke valve 7.12 and balanced valve 7.11 is communicated, B mouthfuls of phase of the other end and liquid controlled reversing main valve 7.7
It is logical.Brake unclasps valve 7.8 and is linked with liquid controlled reversing main valve 7.7, and brake unclasps A mouthfuls of valve 7.8 and motor operates valve group 7
Leakage hydraulic fluid port D is communicated, and brake unclasp valve 7.8 B mouthfuls is communicated with the outlet of pressure-reducing valve 7.1, and brake unclasps P mouthfuls of valve 7.8
It is connected with the throttling end of one-way throttle valve 7.15, S hydraulic fluid port of the one-way throttle valve 7.15 also with motor operation valve group 7 is communicated.
The hydraulic control mouthful of guide's pilot relief valve 7.13 is connected with the entrance of board-like overflow valve 10, the outlet of board-like overflow valve 10
P1 mouthfuls with the first screw thread inserting type shuttle valve 12 is connected.A mouthfuls of first screw thread inserting type shuttle valve 12 and bi-bit bi-pass normally-closed ball valve
A mouthfuls of 13 connection, B mouthfuls of bi-bit bi-pass normally-closed ball valve 13 be connected with the entrance of proportional pressure control valve 11, and proportional pressure control valve 11 goes out
Mouth drain tap respectively with winch motor 8, the leakage hydraulic fluid port D of motor operation valve group 7 and fuel tank 1 are communicated.
P mouthfuls of two-position three-way electromagnetic ball valve 15 is communicated with P2 mouthfuls of the second screw thread inserting type shuttle valve 14, the second thread cartridge
A mouthfuls of formula shuttle valve 14 is communicated with K mouthfuls of the load feedback mouthful of variable delivery hydraulic pump group 3；A mouthfuls of two-position three-way electromagnetic ball valve 15 and motor
The leakage hydraulic fluid port D of valve group 7 is operated to communicate；B mouthfuls of two-position three-way electromagnetic ball valve 15 operates the oil inlet P mouthful phase of valve group 7 with motor
It is logical.
Variable delivery hydraulic pump group 3 uses shaft orientation plunger variable pump, and its variable mode is load-sensitive, invariable power, pressure dam
Control.Variable delivery hydraulic pump group 3 includes that shaft orientation plunger variable pump 3.1, variable delivery hydraulic cylinder 3.2, constant power control valve 3.3, load are quick
Sense valve 3.4, overflow valve 3.5, the orifice plug 3.7 of first throttle plug 3.6 and second.
The inlet port of shaft orientation plunger variable pump 3.1 is communicated with fuel tank 1, the oil-out of shaft orientation plunger variable pump 3.1 respectively with
P mouthfuls of variable delivery hydraulic pump group 3, the rod chamber of variable delivery hydraulic cylinder 3.2 communicates.The piston rod of variable delivery hydraulic cylinder 3.2 respectively with axial direction
The variable swash plate of plunger variable pump 3.1, the spring of constant power control valve 3.3 are connected.
The rod chamber of variable delivery hydraulic cylinder 3.2 respectively with load-sensitive valve 3.4 A mouthfuls, load-sensitive valve 3.4 without spring cavity
Communicate.The entrance respectively with first throttle plug 3.6 of B mouthfuls of load-sensitive valve 3.4, the outlet of constant power control valve 3.3 are communicated, and are born
P mouthfuls of sensitive valve 3.4 outlet respectively with first throttle plug 3.6, the rodless cavity of variable delivery hydraulic cylinder 3.2 is carried to communicate.
The unloading port for exporting respectively with shaft orientation plunger variable pump 3.1 of constant power control valve 3.3, fuel tank 1 are communicated；Invariable power
The entrance outlet respectively with the second orifice plug 3.7 of valve 3.3, the spring cavity of load-sensitive valve 3.4, overflow valve 3.5 is controlled to enter
Mouth is communicated, and the outlet of overflow valve 3.5 is communicated with the outlet of constant power control valve 3.3, entrance and the variable liquid of the second orifice plug 3.7
K mouthfuls of the load feedback mouthful of press pump group 3 is communicated.
The side that cable is led by stepless time adjustment constant tensile control for above-mentioned winch hydraulic system in the embodiment of the present invention
Method, comprises the following steps：
Motor 2 starts, the electromagnet 1DT~equal dead electricity of 5DT, and liquid controlled reversing main valve 7.7 is in middle position, and brake unclasps valve
7.8 link with liquid controlled reversing main valve 7.7, and the rod chamber of brake oil cylinder 9 unclasps valve 7.8 and operates valve group with motor by brake
Leakage oil circuit is communicated, and brake oil cylinder 9 under the action of the spring, is braked to winch motor 8.Electromagnet 5DT is in dead electricity shape
State, variable delivery hydraulic pump group 3 works in pressure and dams variant patterns, and system pressure can gradually rise to variable delivery hydraulic pump group 3 and set
Cutoff pressure, and shaft orientation plunger variable pump 3.1 is in the presence of load-sensitive valve 3.4 and variable delivery hydraulic cylinder 3.2, discharge capacity
The leakage rate of system can be decreased to meet, to ensure the pressure output of systems constant, variable delivery hydraulic pump group 3 is greatly reduced in height
The spillway discharge of pressure, reduces system heat generation, system power dissipation is reduced, so as to improve system effectiveness.
When electromagnet 2DT obtains electric, the pressure oil of variable delivery hydraulic pump group 3 is by check valve 4, pressure-reducing valve 7.1, ratio decompression
Valve 7.3 to liquid controlled reversing main valve 7.7 right-hand member liquid controling cavity, liquid controlled reversing main valve 7.7 in the presence of hydraulic coupling be in right position shape
State, now, the brake linked with liquid controlled reversing main valve 7.7 unclasp valve 7.8 can while act, pressure oil by pressure-reducing valve 7.1,
Brake unclasps valve 7.8 and one-way throttle valve 7.15 enters the rod chamber of brake oil cylinder 9, and brake oil cylinder 9 stops pair twist vehicle and horse
Up to 8 braking action.Pressure oil enters by two-way recuperation valve 7.4, liquid controlled reversing main valve 7.7 and balanced valve 7.11 and twists simultaneously
Vehicle and horse drive winch motor 8 to be in lifting state up to 8.Similarly, when electromagnet 1DT obtains electric, winch motor 8 is driven to be in
Decentralization state.By controlling the size of the electric signal of proportion electro-magnet 1DT, 2DT, opening for liquid controlled reversing main valve 7.7 can be controlled
Mouth amount size, so as to realize carrying out stepless time adjustment to winch motor 8.
One-way throttle valve 7.15 can ensure the fast braking of brake oil cylinder 9, unclamp at a slow speed, prevent liquid controlled reversing main valve 7.7
The phenomenon out of control or unstable that winch motor 8 occurs in commutation.Balanced valve 7.11 can ensure winch motor 8 in decentralization shape
It is unlikely to occur speed due to load excessive during state excessive or out of control.Fill valve 7.14 is in decentralization state in winch motor 8
When, repairing can be carried out to motor, prevent from causing negative pressure because lowering velocity is too fast.
When winch motor 8 is in lifting, decentralization state, electromagnet 5DT obtains electric simultaneously, and load pressure passes through shuttle valve 7.10
And shuttle valve 14 enters into the load feedback mouthful of variable delivery hydraulic pump group 3, variable delivery hydraulic pump group 3 is in load-reacting pattern.Become
Amount hydraulic pressure pump group 3 can automatically be adjusted in the case where output pressure synchronized loading pressure is kept to the discharge capacity of volume adjustable hydraulic pump 3.2
Section, to meet flow velocity control requirement of the winch motor 8 under certain loading condition.Thus, it is possible to reduce the high pressure of system
Overflow, reduces power attenuation, so as to improve system effectiveness.
When electromagnet 2DT, 3DT, 4DT, 5DT obtain electric, system will be in constant tensile control pattern, winch motor 8
Lifting state, variable delivery hydraulic pump group 3 is in load-reacting pattern, and passing ratio overflow valve 11 sets the perseverance of winch motor 8
Tension force value.
Under normal circumstances, the identical tension value of winch motor 8 will remain in setting value, and board-like overflow valve 10 is used to set up load
Pressure overshoot limit value.
When the influence due to wave and ocean current etc. causes load pressure instantaneously to raise, and pressure overshoot amount exceedes plate
During the setting pressure of formula overflow valve 10, the load high pressure of winch motor 8 is by by guide's hydraulic control of guide's pilot relief valve 7.13
Mouth sequentially passes through P1 mouthfuls to A mouthfuls of shuttle valve 12 to board-like overflow valve 10, then by two-way normally-closed ball valve 13, finally opens ratio
Example overflow valve 11, fluid opens overflow flowing, and the damping hole of guide's pilot relief valve 7.13 will produce pressure drop, and make guide's overflow
Valve 7.13 opens overflow, until load pressure overshoot is down to the setting of board-like overflow valve 10, now guide's pilot relief valve
7.13 close overflow, so as to keep the constant tensile control of winch motor 8.Balanced valve 7.11 can ensure that winch motor 8 loads wink
During Shi Shenggao, the feedback pressure of hydraulic variable flow pump group load feedback mouthful keeps constant, and the discharge capacity of Variable plunger pump also remains unchanged.
When the influence due to wave and ocean current etc. causes load pressure instantaneously to decline, balanced valve 7.11 causes that two-way is mended
The outlet pressures for repaying valve 7.4 also decline immediately, and two-way recuperation valve opening will increase, flow-compensated also to increase, and cause to mend
The pressure drop for repaying valve reduces, and the pressure of the side of winch motor 8 will be raised, until the setting value of constant tensile control is reached, so as to ensure
The constant tensile control of winch motor 8.
During the whole constant tensile control of system, variable delivery hydraulic pump group 3 is in load-reacting pattern all the time, except dimension
Hold outside system pressure, the discharge capacity of its plunger variable pump maintains system to control the demand of oil and Leakage Energy, the height of whole system all the time
Pressurized overflow is considerably less, and power loss is substantially reduced, and system effectiveness is improved.
The present invention is not limited to the above-described embodiments, for those skilled in the art, is not departing from
On the premise of the principle of the invention, some improvements and modifications can also be made, these improvements and modifications are also considered as protection of the invention
Within the scope of.The content not being described in detail in this specification belongs to prior art known to professional and technical personnel in the field.
Claims (4)
1. a kind of winch hydraulic system that cable is led by stepless time adjustment constant tensile control, including fuel tank (1), motor (2), variable liquid
Press pump group (3), check valve (4), high-pressure overflow valve (5), backpressure overflow valve (6), motor operate valve group (7), winch motor (8),
Brake oil cylinder (9), board-like overflow valve (10), proportional pressure control valve (11), the first screw thread inserting type shuttle valve (12), the second thread cartridge
Formula shuttle valve (14), bi-bit bi-pass normally-closed ball valve (13) and two-position three-way electromagnetic ball valve (15)；
It is characterized in that：The motor operates the valve group (7) to include pressure-reducing valve (7.1), the first solenoid-operated proportional pressure-reducing valve (7.2), the
Two solenoid-operated proportional pressure-reducing valves (7.3), two-way recuperation valve (7.4), fixed restriction plug (7.5), choke valve (7.6), liquid controlled reversing master
Valve (7.7), brake unclasp valve (7.8), low pressure relief valve (7.9), shuttle valve (7.10), balanced valve (7.11), choke valve
(7.12), guide's pilot relief valve (7.13), Fill valve (7.14) and one-way throttle valve (7.15)；
P mouthfuls of the entrance of the pressure-reducing valve (7.1) and motor operation valve group (7) is communicated, and the outlet of pressure-reducing valve (7.1) is respectively with the
One solenoid-operated proportional pressure-reducing valve (7.2), the entrance of the second solenoid-operated proportional pressure-reducing valve (7.3) are communicated, the first solenoid-operated proportional pressure-reducing valve
(7.2) outlet is communicated with the left position liquid controling cavity of liquid controlled reversing main valve (7.7), the outlet of the second solenoid-operated proportional pressure-reducing valve (7.3)
Communicated with the right position liquid controling cavity of liquid controlled reversing main valve (7.7)；
The leakage hydraulic fluid port of the pressure-reducing valve (7.1) respectively with leakage hydraulic fluid port, second electromagnetism of the first solenoid-operated proportional pressure-reducing valve (7.2)
The leakage hydraulic fluid port of proportional pressure-reducing valve (7.3) is communicated；The leakage hydraulic fluid port of pressure-reducing valve (7.1) also operates the leakage of valve group (7) with motor
Oil circuit is communicated, and the leakage oil circuit of motor operation valve group (7) operates the leakage hydraulic fluid port D and fuel tank (1) phase of valve group (7) by motor
It is logical；
The entrance of the two-way recuperation valve (7.4) is communicated with P mouthfuls of motor operation valve group (7), the outlet of two-way recuperation valve (7.4)
P mouthfuls with liquid controlled reversing main valve (7.7) communicates；The entrance phase of the entrance of fixed restriction plug (7.5) and two-way recuperation valve (7.4)
Logical, the outlet of fixed restriction plug (7.5) is interconnected with the entrance of the entrance of choke valve (7.6), low pressure relief valve (7.9)；Section
The outlet of stream valve (7.6) spring cavity control mouth, the P2 of the first screw thread inserting type shuttle valve (12) respectively with two-way recuperation valve (7.4)
Mouth is communicated；
T mouthfuls of the liquid controlled reversing main valve (7.7) is communicated with T mouthfuls of motor operation valve group (7), the A of liquid controlled reversing main valve (7.7)
Mouth is communicated with the entrance of balanced valve (7.11), and the outlet of balanced valve (7.11) and motor operate A mouthfuls of valve group (7) to communicate；It is described
B mouthfuls of liquid controlled reversing main valve (7.7) is communicated with B mouthfuls of motor operation valve group (7)；
The entrance of guide's pilot relief valve (7.13) is communicated with the outlet of balanced valve (7.11), guide's pilot relief valve
(7.13) entrance of the outlet respectively with motor operation valve group T mouthfuls of (7), Fill valve (7.14) is communicated, Fill valve (7.14)
Export and communicated with B mouthfuls of motor operation valve group (7)；
P1 mouthfuls of the shuttle valve (7.10) is connected with A mouthfuls of liquid controlled reversing main valve (7.7), and P2 mouthfuls of shuttle valve (7.10) is changed with hydraulic control
To B mouthfuls of connection of main valve (7.7)；Outlet, the second thread cartridge respectively with low pressure relief valve (7.9) of A mouthfuls of shuttle valve (7.10)
P1 mouthfuls of connection of formula shuttle valve (14)；
The hydraulic control mouthful of described choke valve (7.12) one end and balanced valve (7.11) is communicated, the other end and liquid controlled reversing main valve (7.7)
B mouthfuls communicate；Brake unclasps valve (7.8) and is linked with liquid controlled reversing main valve (7.7), and brake unclasps A mouthfuls and horse of valve (7.8)
Leakage hydraulic fluid port D up to operation valve group (7) is communicated, and brake unclasp valve (7.8) B mouthful is communicated with the outlet of pressure-reducing valve (7.1), system
Dynamic device unclasp valve (7.8) P mouthfuls is connected with the throttling end of one-way throttle valve (7.15), and one-way throttle valve (7.15) is also grasped with motor
The S hydraulic fluid ports for making valve group (7) are communicated；
The hydraulic control mouthful of guide's pilot relief valve (7.13) is connected with the entrance of board-like overflow valve (10), board-like overflow valve (10)
Outlet be connected with P1 mouthfuls of the first screw thread inserting type shuttle valve (12)；A mouthfuls and two two of first screw thread inserting type shuttle valve (12)
A mouthfuls of connection of logical normally-closed ball valve (13), B mouthfuls of bi-bit bi-pass normally-closed ball valve (13) is connected with the entrance of proportional pressure control valve (11),
The outlet of proportional pressure control valve (11) drain tap respectively with winch motor (8), the leakage hydraulic fluid port D of motor operation valve group (7) and
Fuel tank (1) is communicated；
P mouthfuls of the two-position three-way electromagnetic ball valve (15) is communicated with P2 mouthfuls of the second screw thread inserting type shuttle valve (14), the second screw thread
A mouthfuls of plug-in shuttle valve (14) is communicated with K mouthfuls of the load feedback mouthful of variable delivery hydraulic pump group (3)；Two-position three-way electromagnetic ball valve (15)
A mouthfuls with motor operation valve group (7) leakage hydraulic fluid port D communicate；B mouthfuls of two-position three-way electromagnetic ball valve (15) operates valve group with motor
(7) oil inlet P mouthful is communicated.
2. the winch hydraulic system of cable is led by stepless time adjustment constant tensile control as claimed in claim 1, it is characterised in that：Institute
Motor (2) is stated to be connected with variable delivery hydraulic pump group (3), the oil-out P of variable delivery hydraulic pump group (3) entrance respectively with check valve (4),
The entrance of high-pressure overflow valve (5) is connected, and the outlet of check valve (4) is connected with the oil inlet P of motor operation valve group (7)；Motor is grasped
Make valve group (7) oil return inlet T be connected with the outlet of high-pressure overflow valve (5) after be connected with fuel tank (1) by backpressure overflow valve (6).
3. the winch hydraulic system of cable is led by stepless time adjustment constant tensile control as claimed in claim 1, it is characterised in that：Institute
The oil inlet for stating winch motor (8) is connected with A mouthfuls of motor operation valve group (7), and oil return opening and the motor of winch motor (8) are operated
B mouthfuls of valve group (7) is connected, and the rod chamber of brake oil cylinder (9) is connected with the S hydraulic fluid ports of motor operation valve group (7).
4. the winch hydraulic system that cable is led by stepless time adjustment constant tensile control as described in any one of claims 1 to 3, it is special
Levy and be：The variable delivery hydraulic pump group (3) includes shaft orientation plunger variable pump (3.1), variable delivery hydraulic cylinder (3.2), power limitation control
Valve (3.3), load-sensitive valve (3.4), overflow valve (3.5), first throttle plug (3.6) and the second orifice plug (3.7)；
The inlet port of the shaft orientation plunger variable pump (3.1) is communicated with fuel tank (1), the oil-out of shaft orientation plunger variable pump (3.1)
Respectively with variable delivery hydraulic pump group (3) P mouthfuls, the rod chamber of variable delivery hydraulic cylinder (3.2) communicates；The piston of variable delivery hydraulic cylinder (3.2)
Bar variable swash plate respectively with shaft orientation plunger variable pump (3.1), the spring of constant power control valve (3.3) are connected；
The rod chamber of the variable delivery hydraulic cylinder (3.2) A mouthfuls, the nothing of load-sensitive valve (3.4) respectively with load-sensitive valve (3.4)
Spring cavity is communicated；Entrance, the constant power control valve (3.3) respectively with first throttle plug (3.6) of B mouthfuls of load-sensitive valve (3.4)
Outlet communicate, P mouthfuls of load-sensitive valve (3.4) outlet respectively with first throttle plug (3.6), variable delivery hydraulic cylinder (3.2)
Rodless cavity is communicated；
The outlet of the constant power control valve (3.3) unloading port respectively with shaft orientation plunger variable pump (3.1), fuel tank (1) are communicated；
The outlet respectively with the second orifice plug (3.7) of the entrance of constant power control valve (3.3), the spring cavity of load-sensitive valve (3.4), overflow
The entrance of stream valve (3.5) is communicated；The outlet of overflow valve (3.5) is communicated with the outlet of constant power control valve (3.3), the second orifice plug
(3.7) entrance is communicated with K mouthfuls of the load feedback mouthful of variable delivery hydraulic pump group (3).
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| CN201510372268.2A CN104925685B (en) | 2015-06-30 | 2015-06-30 | A kind of winch hydraulic system that cable is led by stepless time adjustment constant tensile control |
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