CN104444816B - Hydraulic control system of hoisting machinery and hoisting machinery - Google Patents
Hydraulic control system of hoisting machinery and hoisting machinery Download PDFInfo
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- CN104444816B CN104444816B CN201410520918.9A CN201410520918A CN104444816B CN 104444816 B CN104444816 B CN 104444816B CN 201410520918 A CN201410520918 A CN 201410520918A CN 104444816 B CN104444816 B CN 104444816B
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- 238000013016 damping Methods 0.000 claims abstract description 47
- 230000009471 action Effects 0.000 claims abstract description 25
- 239000003921 oil Substances 0.000 claims description 133
- 239000012530 fluid Substances 0.000 claims description 45
- 239000010720 hydraulic oil Substances 0.000 claims description 44
- 230000000630 rising effect Effects 0.000 claims description 13
- 230000008859 change Effects 0.000 claims description 6
- 239000000446 fuel Substances 0.000 claims description 6
- 238000005096 rolling process Methods 0.000 claims description 2
- 230000000694 effects Effects 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 239000000725 suspension Substances 0.000 description 4
- 230000007812 deficiency Effects 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 238000005303 weighing Methods 0.000 description 1
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C13/00—Other constructional features or details
- B66C13/18—Control systems or devices
- B66C13/20—Control systems or devices for non-electric drives
-
- 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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Fluid-Pressure Circuits (AREA)
- Types And Forms Of Lifts (AREA)
Abstract
The invention relates to the technical field of hoisting machinery, and discloses a hydraulic control system of the hoisting machinery and the hoisting machinery. In order to prevent the phenomenon that the oil supply of the hoisting motor is insufficient, the hydraulic control system comprises a boom stretching control system for controlling the stretching and retracting actions of a stretching oil cylinder of the boom, a hoisting control system for controlling the rope stretching and retracting actions of the hoisting motor, and a variable pump shared by the boom stretching control system and the hoisting control system, and further comprises: the switching valve group comprises a reversing valve and a first damping element, the reversing valve comprises a control oil port, a working oil port and an oil return port, and the control oil port of the reversing valve is connected with the oil outlet of the arm retracting control valve through the first damping element; two oil inlets of the first shuttle valve are respectively connected with oil outlets of the hoisting control valve and the hoisting falling control valve, and an oil outlet of the first shuttle valve is connected with a working oil port of the reversing valve.
Description
Technical field
The present invention relates to hoisting machinery technical field, particularly relate to hydraulic control system and the one of a kind of hoisting machinery
Hoisting machinery.
Background technology
Hoisting machinery, the autocrane of the most medium and small tonnage, generally comprise following a few class hydraulic control system: arm
Telescopic control system, winch control system, luffing control system, rotary control system, counterweight Lifting Control System and air-conditioning
Control system etc..Existing hoisting arm expansion control system and winch control system share a variable pump, and variable pump is from hydraulic oil container
Middle extract force feed is to hoisting arm expansion control system and winch control system fuel feeding.
In hoisting arm expansion control system, including flexible control crank, telescopic oil cylinder, and telescopic hydraulic valve, flexible behaviour
Vertical handle controls the action of telescopic oil cylinder through telescopic hydraulic valve, specifically includes: flexible control crank when semi-girder position, variable
The hydraulic oil of pump input enters the rodless cavity of telescopic oil cylinder through telescopic hydraulic valve, and the hydraulic oil of simultaneous retractable cylinder rod chamber is through stretching
Contracting hydraulic valve flows back to hydraulic oil container, and telescopic oil cylinder realizes stretching out of expansion link；Flexible control crank when contracting arm position, variable pump
The hydraulic oil of input enters the rod chamber of telescopic oil cylinder through telescopic hydraulic valve, and the hydraulic oil of simultaneous retractable oil cylinder rodless cavity is through flexible
Hydraulic valve flows back to hydraulic oil container, and telescopic oil cylinder realizes the retraction of expansion link.
In winch control system, including elevator control crank, hoist motor, and elevator hydraulic valve, elevator handles hands
Handle controls the action of hoist motor through elevator hydraulic valve, specifically includes: elevator control crank when hoisting crane position, variable pump
The hydraulic oil of input enters the hydraulic fluid port that hoists of hoist motor, the hydraulic oil warp of oil-falling port under hoist motor simultaneously through elevator hydraulic valve
Elevator hydraulic valve flows back to hydraulic oil container, and now elevator rope closing realizes hoisting of suspension hook；Elevator control crank when elevator dropping place is put,
The hydraulic oil of variable pump input enters the lower oil-falling port of hoist motor through elevator hydraulic valve, and hoist motor hoists the liquid of hydraulic fluid port simultaneously
Force feed flows back to hydraulic oil container through elevator hydraulic valve, and elevator is put rope and realized the whereabouts of suspension hook.Hoisting arm expansion control crank and elevator behaviour
Vertical handle can simultaneously action, thus realize elevator and rise and fall and the composite move of hoisting arm expansion.
Telescopic oil cylinder includes rod chamber and rodless cavity, includes action bars in rod chamber, and therefore the cross-sectional area of rod chamber is wanted
Less than the cross-sectional area of rodless cavity, it is assumed that the cross-sectional area of rod chamber is AThere is bar, the cross-sectional area of rodless cavity is AWithout bar, rodless cavity with
The cross-sectional area of rod chamber is much larger than 1 than for A, A, when telescopic oil cylinder carries out retract action, enters the hydraulic pressure of cylinder rod chamber
The specified output flow Q that flow is variable pump of oil, due to the existence of telescopic oil cylinder rodless cavity Yu area ratio A of rod chamber, then
It is A*Q that telescopic oil cylinder flow back into the flow of the hydraulic oil of hydraulic oil container from rodless cavity so that telescopic oil cylinder retract time without bar
The flow in chamber is very big so that the pipeline connecting telescopic oil cylinder rodless cavity do the biggest.For solving to connect telescopic oil cylinder without bar
The problem that lumen road is the biggest, is typically limited variable pump by telescopic hydraulic valve and enters the flow of telescopic oil cylinder rod chamber as Q1,
The i.e. hydraulic oil of variable pump output cannot be all by telescopic hydraulic valve, and variable pump performance characteristic determines its now variable pump
Output flow is Q1Hydraulic oil, and Q1It is far smaller than the specified output flow Q of variable pump.
During arm is retracted, if arm is retracted after stopping carries out the action that hoisting crane or elevator fall at full speed immediately,
The output flow of variable pump will be from Q1Increase to metered flow Q of variable pump immediately to meet the demand of elevator action, but become
Amount POF is from Q1Increasing to Q and need regular hour t, interior during this period, hoist motor actual demand flow is Q, therefore
In time t, hoist motor there will be the phenomenon for shortage of oil, causes the fault rate of hoist motor in hoisting system higher, very
To the damage causing hoist motor.
Summary of the invention
The invention provides the hydraulic control system of a kind of hoisting machinery and a kind of hoisting machinery, in order to prevent hoist motor
Phenomenon for shortage of oil occurs, and then reduces the fault rate of hoist motor.
First the embodiment of the present invention provides the hydraulic control system of a kind of hoisting machinery, including: control the flexible oil of arm
The hoisting arm expansion control system of cylinder expanding-contracting action, described hoisting arm expansion control system includes contracting arm control valve and semi-girder control valve；
Controlling the winch control system of hoist motor retractable rope action, described winch control system includes that hoisting crane control valve and elevator fall
Control valve；The variable pump that described hoisting arm expansion control system and described winch control system share, for described hoisting arm expansion
Control system and described winch control system fuel feeding, described hydraulic control system also includes:
Switching valve group, including reversal valve and the first damping element, described reversal valve includes control port, actuator port and returns
Hydraulic fluid port, the control port of described reversal valve is connected through the oil-out of described first damping element with described contracting arm control valve, described
Reversal valve has cut-off position and the hydraulic oil that flows into through the control port of described reversal valve and makes what described reversal valve turned on to lead
Logical position, when described reversal valve is on, the actuator port of described reversal valve is connected with the oil return opening of described reversal valve；
First shuttle valve, two oil-ins of described first shuttle valve fall with described hoisting crane control valve and elevator control valve respectively
Oil-out be connected, the oil-out of described first shuttle valve is connected with the actuator port of described reversal valve.
In technical solution of the present invention, hydraulic control system adds switching valve group and the first shuttle valve, when contracting arm control
During valve processed conducting, the pressure oil of contracting arm control valve oil-out is divided into two-way, retracts for the expansion link controlling telescopic oil cylinder in a road,
Commutate to operating position for controlling reversal valve through the control mouth of the first damping element to reversal valve in one tunnel, the working position of reversal valve
It is set to turn on position, the relatively low flow Q that now variable pump output sets1, when contracting arm stops, i.e. contracting arm control valve disconnects, by
In the existence of the first damping element, reversal valve needs through could reset after a while (reversal valve is in cut-off position after resetting),
The operation that contracting arm carries out hoisting crane when stopping immediately or elevator falls, i.e. hoisting crane control valve or elevator fall control valve conducting, due to
The effect of the first shuttle valve, hoisting crane control valve or elevator fall control valve oil-out pressure oil can through first shuttle valve enter change
To valve, owing to reversal valve needs could reset through after a while, therefore variable pump has time enough from exporting relatively low stream
Amount Q1Increase to metered flow Q, therefore, it is to avoid the hoist motor that variable pump output flow deficiency causes being asked for shortage of oil
Topic, and then reduce the fault rate of hoist motor.
Preferably, described switching valve group also includes the second damping element, and the oil-out of described first shuttle valve is through described second
Damping element is connected with the actuator port of described reversal valve.
In this embodiment, due to the existence of the second damping element so that hoisting crane control valve or elevator fall control valve
The pressure of the pressure oil of oil-out can reduce accordingly, and then the flow of the current desired pressure oil of hoist motor is reduced, and enters
And improve elevator rise and fall operation stability.
Described hoisting arm expansion control system and winch control system include various ways, and one of which hoisting arm expansion controls system
System is particularly as follows: described hoisting arm expansion control system also includes flexible hydraulic control operating valve set, and described flexible hydraulic control operating valve set includes
Flexible reversal valve, described flexible reversal valve include the first oil-in, elongation control port, retraction control port, the first work
Hydraulic fluid port, the second actuator port and the first oil return opening, the first oil-in of described flexible reversal valve is connected with described variable pump, described
First actuator port and the second actuator port are connected with rodless cavity and the rod chamber of described telescopic oil cylinder respectively, described flexible commutation
The elongation control port of valve is connected with the oil-out of described semi-girder control valve, the retraction control port of described flexible reversal valve and institute
The oil-out stating contracting arm control valve is connected, and described flexible reversal valve has to be made through the hydraulic oil of described retraction control port inflow
The first of described flexible reversal valve conducting turns on position and makes described flexible through the hydraulic oil of described elongation control port inflow
Second conducting position of reversal valve conducting, when described flexible reversal valve is in the first conducting position, the first of described flexible reversal valve
Oil-in and the second actuator port are connected and the first actuator port and the first oil return opening are connected so that telescopic oil cylinder flexible
Bar is retracted, when flexible reversal valve is in the second conducting position, and the first oil-in of described flexible reversal valve and the first actuator port
It is connected and the second actuator port and the first oil return opening are connected so that the expansion link elongation of telescopic oil cylinder；
One of which winch control system is particularly as follows: described winch control system also includes hydraulic control operating valve set of rising and falling, institute
State hydraulic control operating valve set of rising and falling and include the reversal valve that rises and falls, described in rise and fall reversal valve include the second oil-in, lift control hydraulic fluid port,
Whereabouts control port, the 3rd actuator port, the 4th actuator port and the second oil return opening, described in rise and fall reversal valve the second oil-in with
Described variable pump be connected, described 3rd actuator port and the 4th actuator port respectively with described hoist motor hoist hydraulic fluid port and under
Oil-falling port is connected, described in the lift control hydraulic fluid port of reversal valve that rises and falls be connected with the oil-out of described hoisting crane control valve, described
Fall with the described elevator oil-out of control valve of the whereabouts control port of reversal valve of falling is connected, described in the reversal valve that rises and falls have through described
Hydraulic oil that lift control hydraulic fluid port flows into and the 3rd conducting position of reversal valve conducting of rising and falling described in making and fall to controlling through described
Hydraulic oil that hydraulic fluid port flows into and the 4th conducting position of reversal valve conducting of rising and falling described in making, lead when the described reversal valve that rises and falls is in the 3rd
During logical position, described in rise and fall reversal valve the second oil-in and the 3rd actuator port is connected and the 4th actuator port and the second oil return
Mouthful be connected so that hoist motor is carried out hoisting action, when the reversal valve that rises and falls is in the 4th conducting position, described in rise and fall reversal valve
The second oil-in and the 4th actuator port is connected and the 3rd actuator port and the second oil return opening are connected so that hoist motor
Carry out drop action.
In above-mentioned hoisting arm expansion control system, described flexible reversal valve also includes the 5th actuator port and the 6th working oil
Mouthful, described hoisting arm expansion control system also includes that the first pressure-compensated valve, described first pressure-compensated valve include oil-in, work
Hydraulic fluid port, oil return opening and control port, the oil-in of described first pressure-compensated valve and control port respectively with described flexible commutation
5th actuator port of valve is connected, the actuator port of described first pressure-compensated valve and the 6th working oil of described flexible reversal valve
Mouthful be connected, described first pressure-compensated valve have through described first pressure-compensated valve control port flow into hydraulic oil and make institute
Stating the conducting position of the first pressure-compensated valve conducting, when described first pressure-compensated valve is on, described first pressure is mended
The oil-in repaying valve is connected with actuator port and the oil return opening of described first pressure-compensated valve respectively, wherein, described when flexible
When reversal valve is in the first conducting position, the first oil-in of described flexible reversal valve and the second actuator port are connected specially
One oil-in and the 5th actuator port are connected, and the 6th actuator port and the second actuator port are connected；Described when flexible commutation
When valve is in the second conducting position, the first oil-in of described flexible reversal valve and the first actuator port are connected and specially first enter
Hydraulic fluid port and the 5th actuator port are connected, and the 6th actuator port and the first actuator port are connected；
The described reversal valve that rises and falls also includes that the 7th actuator port and the 8th actuator port, described winch control system also include
Second pressure-compensated valve, described second pressure-compensated valve includes oil-in, actuator port, oil return opening and control port, described
The oil-in of two pressure-compensated valves with control port respectively the 7th actuator port with the described reversal valve that rises and falls be connected, described second
The actuator port of pressure-compensated valve is connected with the 8th actuator port of the described reversal valve that rises and falls, and described second pressure-compensated valve has
Through described second pressure-compensated valve control port flow into hydraulic oil and make described second pressure-compensated valve conducting conducting position,
When described second pressure-compensated valve is on, the oil-in of described second pressure-compensated valve respectively with described second pressure
The actuator port of recuperation valve is connected with oil return opening, wherein, described when the reversal valve that rises and falls be in the 3rd conducting position time, described in rise and fall
Second oil-in of reversal valve and the 3rd actuator port are connected the specially second oil-in and the 7th actuator port is connected, and
Eight actuator ports and the 3rd actuator port are connected；Described when the reversal valve that rises and falls is in the 4th conducting position, described in rise and fall commutation
Second oil-in of valve and the 4th actuator port are connected the specially second oil-in and the 7th actuator port is connected, the 8th work
Make hydraulic fluid port and the 4th actuator port is connected.
In above-mentioned winch control system, described winch control system also includes the second shuttle valve and the volume controlling elevator switch
Raise brake valve, two oil-ins of described second shuttle valve respectively with described hoist motor hoist hydraulic fluid port and lower oil-falling port is connected,
The oil-out of described second shuttle valve is connected with the control port of described elevator brake valve；
The actuator port of described elevator brake valve is connected with the actuator port of the brake of described hoist motor.
In above-mentioned winch control system, described winch control system also includes the oil that hoists being arranged at described hoist motor
Elevator balanced valve between mouth and lower oil-falling port.
The version of elevator balanced valve has multiple, and described elevator balanced valve includes check valve and sequence valve, described unidirectional
Valve is arranged at the oil port that hoists of described hoist motor, two actuator ports of described sequence valve respectively with the entering of described check valve
Hydraulic fluid port is connected with oil-out, and guide's hydraulic fluid port of described sequence valve is connected with the lower oil-falling port of described hoist motor.
In above-mentioned hoisting arm expansion control system, described hoisting arm expansion control system also includes being arranged at described telescopic oil cylinder
Rodless cavity and rod chamber between flexible balanced valve.
The version of flexible balanced valve has multiple, and described flexible balanced valve includes bi-bit bi-pass reversal valve and the 3rd damping
Element, described bi-bit bi-pass reversal valve includes control port and two actuator ports, the control oil of described bi-bit bi-pass reversal valve
Mouth is connected with described rod chamber through described 3rd damping element, and two actuator ports of described bi-bit bi-pass reversal valve are serially connected with institute
Stating between the actuator port of rodless cavity and described flexible reversal valve, described bi-bit bi-pass reversal valve has the 5th conducting position and the 6th
Conducting position, when described bi-bit bi-pass reversal valve is in the 5th conducting position, two actuator port one-way conductions, when described two two
When logical reversal valve is in the 6th conducting position, two actuator port damping conductings, wherein, described one-way conduction is led with damping conducting
Logical in opposite direction.
The embodiment of the present invention also provides for a kind of hoisting machinery, including the hydraulic control system of any of the above-described kind of hoisting machinery.By
In using the hydraulic control system of any of the above-described kind of hoisting machinery in hoisting machinery, it is therefore prevented that stop entering immediately at contracting arm
Row hoisting crane or elevator fall the hoist motor that causes when the operating problem for shortage of oil, and then reduce the fault rate of hoist motor.
Heretofore described hoisting machinery can be various structures form, preferably wheeled crane.
Accompanying drawing explanation
The structural representation of the hydraulic control system of the hoisting machinery that Fig. 1 provides for first embodiment of the invention；
Fig. 2 is the structural representation that the reversal valve in the hydraulic control system shown in Fig. 1 is on position；
Fig. 3 is the structural representation that the reversal valve in the hydraulic control system shown in Fig. 1 is in cut-off position；
Fig. 4 is the structural representation of the flexible reversal valve in the hydraulic control system shown in Fig. 1；
The structural representation of the hydraulic control system of the hoisting machinery that Fig. 5 provides for second embodiment of the invention；
Fig. 6 is flexible reversal valve and the structural representation of the first pressure-compensated valve in the hydraulic control system shown in Fig. 5；
Fig. 7 is rise and fall in the hydraulic control system shown in Fig. 5 reversal valve and the structural representation of the second pressure-compensated valve；
Fig. 8 is the structural representation of the elevator balanced valve in the hydraulic control system shown in Fig. 5；
Fig. 9 is the structural representation of the flexible balanced valve in the hydraulic control system shown in Fig. 5.
Reference:
1-telescopic oil cylinder 4-variable pump 5-switches valve group 6-the first shuttle valve
7-hoist motor 8-hydraulic oil container 9-brake 10-elevator brake valve
11-rod chamber 12-rodless cavity 21-contracting arm control valve 22-semi-girder control valve
23-reversal valve 24-the first pressure-compensated valve 25-that stretches stretches balanced valve 31-hoisting crane control valve
32-elevator control valve 33-that falls is risen and fallen reversal valve 34-the second pressure-compensated valve 35-elevator balanced valve
36-the second shuttle valve 51-reversal valve 52-the first damping element 53-the second damping element
351-check valve 352-sequence valve 251-bi-bit bi-pass reversal valve 252-the 3rd damping element
Detailed description of the invention
In order to prevent hoist motor from the phenomenon for shortage of oil occurring, embodiments provide the liquid of a kind of hoisting machinery
Pressure control system and a kind of hoisting machinery.In this technical scheme, hydraulic control system adds switching valve group and the first shuttle
Valve, when contracting arm control valve turns on, the pressure oil of contracting arm control valve oil-out is divided into two-way, and a road is for controlling telescopic oil cylinder
Expansion link is retracted, and commutating to operating position for controlling reversal valve through the control mouth of the first damping element to reversal valve in a road, changes
To the operating position of valve for conducting position, the relatively low flow Q that now variable pump output sets1, when contracting arm stops, i.e. contracting arm control
Valve processed disconnects, and due to the existence of the first damping element, reversal valve needs (to locate after reversal valve reset through resetting after a while
In cut-off position), carry out hoisting crane immediately during the stopping of contracting arm or operation that elevator falls, i.e. hoisting crane control valve or elevator falls control valve
Conducting, due to the effect of the first shuttle valve, hoisting crane control valve or elevator fall the pressure oil of oil-out of control valve can be through first
Shuttle valve enters the actuator port of reversal valve, and owing to reversal valve needs could reset through after a while, therefore variable pump has enough
Time from the relatively low flow Q of output1Increase to metered flow Q, therefore, it is to avoid the volume that variable pump output flow deficiency causes
Raise the motor problem for shortage of oil, and then reduce the fault rate of hoist motor.For making the purpose of the present invention, technical scheme and excellent
Point is clearer, is described in further detail the present invention by the following examples.
First the embodiment of the present invention provides the hydraulic control system of a kind of hoisting machinery, as it is shown in figure 1, Fig. 1 is the present invention
The structural representation of the hydraulic control system of the hoisting machinery that first embodiment provides, the O shown in Fig. 1 is for controlling oil sources, this liquid
Pressure control system includes: control the hoisting arm expansion control system of telescopic oil cylinder 1 expanding-contracting action of arm, hoisting arm expansion control system
Including contracting arm control valve 21 and semi-girder control valve 22；Control the winch control system of hoist motor 7 retractable rope action, rolling control
System includes that hoisting crane control valve 31 and elevator fall control valve 32；The change that hoisting arm expansion control system and winch control system share
Amount pump 4, for hoisting arm expansion control system and winch control system fuel feeding, this hydraulic control system also includes:
Switching valve group 5, including reversal valve 51 and the first damping element 52, reversal valve 51 includes control port A1, working oil
Mouth A3With oil return opening A2, the control port A of reversal valve 511It is connected through the oil-out of the first damping element 52 with contracting arm control valve 21,
Reversal valve 51 has cut-off position and the control port A through reversal valve 511The hydraulic oil that flows into and make what reversal valve 51 turned on to lead
Logical position, when reversal valve 51 is on, the actuator port A of reversal valve 513Oil return opening A with reversal valve 512It is connected；
First shuttle valve 6, two oil-in (B of the first shuttle valve 61And B2) fall control respectively with hoisting crane control valve 31 and elevator
The oil-out of valve 32 processed is connected, the oil-out B of the first shuttle valve 63Actuator port A with reversal valve 513It is connected.
In technical solution of the present invention, hydraulic control system adds switching valve group 5 and the first shuttle valve 6, when contracting arm
When control valve 21 turns on, the pressure oil of contracting arm control valve 21 oil-out is divided into two-way, and a road is for controlling the flexible of telescopic oil cylinder 1
Bar is retracted, and a road is for the control mouth A through the first damping element 52 to reversal valve 511Control reversal valve 51 to commutate to working position
Putting, the operating position of reversal valve 51 is conducting position, the relatively low flow Q that now variable pump 4 output sets1, when contracting arm stops,
I.e. contracting arm control valve 21 disconnects, and due to the existence of the first damping element 52, reversal valve 51 needs could reset through after a while
(reversal valve 51 is in cut-off position after resetting), carries out hoisting crane during the stopping of contracting arm or operation that elevator falls immediately, i.e. elevator starts to control
Valve 31 processed or the elevator control valve 32 that falls turns on, and due to the effect of the first shuttle valve 6, hoisting crane control valve 31 or elevator fall control valve 32
The pressure oil of oil-out can enter the actuator port A of reversal valve 51 through the first shuttle valve 63, due to reversal valve 51 need through
A period of time could reset, and therefore variable pump 4 has time enough from exporting relatively low flow Q1Increase to metered flow Q, because of
This, it is to avoid the hoist motor that variable pump output flow deficiency causes is for the problem of shortage of oil, and then reduces hoist motor
Fault rate.
Preferably, switching valve group 5 also includes the second damping element 53, and the oil-out of the first shuttle valve 6 is through the second damping element
53 and the actuator port A of reversal valve 513It is connected.
In this embodiment, due to the existence of the second damping element 53 so that hoisting crane control valve 31 or elevator fall to controlling
The pressure of the pressure oil of the oil-out of valve 32 can reduce accordingly, and then makes the flow of the current desired pressure oil of hoist motor 7
Reduce, improve elevator rise and fall operation stability.
In the inventive solutions, contracting arm control valve 21, semi-girder control valve 22, hoisting crane control valve 31 and elevator fall
Control valve 32 all preferably employs the proportional pressure-reducing valve shown in Fig. 1, and proportional pressure-reducing valve can be as the switch of respective channels, and can
Size and then the governing speed of control valve opening is come with the spring of the set pressure of passing ratio air relief valve.
Continue referring to shown in Fig. 1, in the inventive solutions, include in hoisting arm expansion control system flexible flat
Weighing apparatus valve 25, includes elevator balanced valve 35 at winch control system, and the load feedback mouth of variable pump 4 need to be connected to by overflow valve
On oil return line.
Continue referring to shown in Fig. 1, in technical solution of the present invention, adjust the size of the first damping element 52 damping, can
To adjust the resetting time of reversal valve 51, it is used for meeting the output flow of variable pump from relatively low Q1Increase to the time needed for Q；
Adjust the size of the second damping element 53 damping, the size of the flow of the current desired pressure oil of hoist motor 7 can be adjusted, use
Limit the maximum operating speed of hoist motor in the resetting time of reversal valve 51.Those skilled in the art can be according to actual warp
Testing the adjustment of the size carrying out the first damping element 52 and the second damping element 53, the present invention does not limit concrete numerical value.
As shown in Figures 2 and 3, the reversal valve during Fig. 2 is the hydraulic control system shown in Fig. 1 is on the structure of position and shows
Being intended to, Fig. 3 is the structural representation that the reversal valve in the hydraulic control system shown in Fig. 1 is in cut-off position, as in figure 2 it is shown, contracting
The pressure oil of arm control valve oil-out is through the control mouth A of the first damping element 52 to reversal valve 511, reversal valve 51 commutation is to work
Position, is i.e. on position, enters the work of reversal valve 51 through the second damping element 53 from the pressure oil of the oil-out of the first shuttle valve
Make hydraulic fluid port A3, through oil return opening A2It is back to hydraulic oil container；As it is shown on figure 3, after contracting arm stops, controlling mouth A1Oil pressure slowly drop
Low, reversal valve 51 recovers to ending position through after a while.
Continuing referring to shown in Fig. 1, the first shuttle valve 6 can use two check valves to replace, if the first shuttle valve 6 is two lists
To valve, then the oil-in of one of them check valve is connected with the oil-out of hoisting crane control valve 31, the oil-feed of another check valve
The oil-out of the control valve 32 that falls mouthful with elevator is connected, and the oil-out of two check valves is all connected with the second damping element 53.
Hoisting arm expansion control system and winch control system include various ways, and one of which hoisting arm expansion control system has
Body is: continue referring to shown in Fig. 1, and hoisting arm expansion control system also includes that flexible hydraulic control operating valve set, flexible hydraulic control handle valve
Group includes that flexible reversal valve 23, flexible reversal valve 23 include the first oil-in C2, elongation control port C6, retraction control port C5、
First actuator port C1, the second actuator port C3With the first oil return opening C4, the first oil-in C of flexible reversal valve 232With variable pump
4 are connected, the first actuator port C1With the second actuator port C3It is connected with rodless cavity 12 and the rod chamber 11 of telescopic oil cylinder 1 respectively, stretches
The elongation control port C of contracting reversal valve 236Being connected with the oil-out of semi-girder control valve 22, the retraction of flexible reversal valve 23 controls oil
Mouth C5Being connected with the oil-out of contracting arm control valve 21, flexible reversal valve 23 has through retraction control port C5Flow into hydraulic oil and
Make the first conducting position of flexible reversal valve 23 conducting and through elongation control port C6The hydraulic oil that flows into and make flexible reversal valve
Second conducting position of 23 conductings, when flexible reversal valve 23 is in the first conducting position, the first oil-in C of flexible reversal valve 232
With the second actuator port C3It is connected and the first actuator port C1With the first oil return opening C4It is connected so that stretching of telescopic oil cylinder 1
Bar is retracted, when flexible reversal valve 23 is in the second conducting position, and the first oil-in C of flexible reversal valve 232With the first working oil
Mouth C1It is connected and the second actuator port C3With the first oil return opening C4It is connected so that the expansion link elongation of telescopic oil cylinder；
One of which winch control system is particularly as follows: continue referring to shown in Fig. 1, and winch control system also includes the liquid that rises and falls
Control operating valve set, hydraulic control operating valve set of rising and falling includes the reversal valve 33 that rises and falls, the reversal valve 33 that rises and falls include the second oil-in D2, rise
Rise control port D5, whereabouts control port D6, the 3rd actuator port D3, the 4th actuator port D1With the second oil return opening D4(D1、D2With
D3), rise and fall reversal valve 33 second oil-in D2It is connected with variable pump 4, the 3rd actuator port D3With the 4th actuator port D1Respectively with
The hydraulic fluid port E that hoists of hoist motor 71With lower oil-falling port E2It is connected, the lift control hydraulic fluid port D of the reversal valve 33 that rises and falls5With hoisting crane control
The oil-out of valve 31 is connected, the whereabouts control port D of the reversal valve 33 that rises and falls6The oil-out of the control valve that falls with elevator 32 is connected, and rises
The reversal valve 33 that falls has through lift control hydraulic fluid port D5The hydraulic oil and making flowed into rise and fall reversal valve 33 conducting the 3rd conducting position with
And through whereabouts control port D6The hydraulic oil and making flowed into rises and falls the 4th conducting position of reversal valve 33 conducting, when the reversal valve 33 that rises and falls
When being in the 3rd conducting position, the second oil-in D of the reversal valve 33 that rises and falls2With the 3rd actuator port D3It is connected and the 4th working oil
Mouth D1With the second oil return opening D4It is connected so that hoist motor 7 is carried out hoisting action, and when rising and falling, reversal valve 33 is in the 4th conducting
During position, the second oil-in D of the reversal valve 33 that rises and falls2With the 4th actuator port D1It is connected and the 3rd actuator port D3With second time
Hydraulic fluid port D4It is connected so that hoist motor 7 carries out drop action.
Continuing referring to shown in Fig. 1, the structure of flexible reversal valve 23 and the reversal valve 33 that rises and falls can have multiple, in the present invention
Illustrating the operation principle of flexible reversal valve 23 as a example by three position four-way directional control valve, as shown in Figure 4, Fig. 4 is shown in Fig. 1
The structural representation of the flexible reversal valve in hydraulic control system, refer to shown in Fig. 1 and Fig. 4, in flexible reversal valve 23 first
Oil return opening C4It is connected with hydraulic oil container 8, the first oil-in C of flexible reversal valve 232It is connected with the oil-out of variable pump 4, the second work
Make hydraulic fluid port C3It is connected with the rod chamber 11 of telescopic oil cylinder 1, the first actuator port C1It is connected with the rodless cavity 12 of telescopic oil cylinder 1, flexible
The elongation control port C of reversal valve 236It is connected with the oil-out of semi-girder control valve 22, the retraction control port of flexible reversal valve 23
C5It is connected with the oil-out of contracting arm control valve 21.As a example by contracting arm, when contracting arm control valve 21 turns on, going out of contracting arm control valve 21
The oil that hydraulic fluid port flows out controls flexible reversal valve 23 and commutates to the first operating position (the i.e. first conducting position), the pressure that variable pump 4 provides
Power oil is from the first oil-in C2With the second actuator port C3Enter rod chamber 11, from the oil of rodless cavity 12 outflow through the first working oil
Mouth C1With the first oil return opening C4Flow back into hydraulic oil container 8, complete the retract action of expansion link.During semi-girder, flexible reversal valve 23 commutates
To the second operating position (the i.e. second conducting position), similar with said process, complete the elongation action of expansion link.Flexible reversal valve 23
When being in middle position, the oil in the pipeline that telescopic oil cylinder 1 is connected with flexible reversal valve 23 can be made to be back in hydraulic oil container 8.
Rising and falling reversal valve 33 can also be for three position four-way directional control valve, operation principle and the operation principle class of flexible reversal valve 23
Seemingly, repeat the most one by one.
Flexible hydraulic control operating valve set and hydraulic control operating valve set of rising and falling are parallel structure, and variable pump is grasped to flexible hydraulic control simultaneously
Vertical valve group and each performer (such as telescopic oil cylinder, the hoist motor) fuel feeding risen and fallen in hydraulic control operating valve set, each hydraulic control is handled
The inlet flow rate of valve group is equal to the output flow of variable pump.Visible, easily there is hoist motor in parallel hydraulic control system
The problem of low on fuel, therefore, technical scheme is particularly suitable in the hydraulic control system of said structure.
As shown in Figure 5 and Figure 6, the knot of the hydraulic control system of the hoisting machinery that Fig. 5 provides for second embodiment of the invention
Structure schematic diagram, Fig. 6 is flexible reversal valve and the structural representation of the first pressure-compensated valve in the hydraulic control system shown in Fig. 5,
In above-mentioned hoisting arm expansion control system, flexible reversal valve 23 also includes the 5th actuator port C7With the 6th actuator port C8, arm
Telescopic control system also includes that the first pressure-compensated valve 24, the first pressure-compensated valve 24 include oil-in F1, actuator port F3, return
Hydraulic fluid port F4With control port F2, the oil-in F of the first pressure-compensated valve 241With control port F2Respectively with flexible reversal valve 23
5th actuator port C7It is connected, the actuator port F of the first pressure-compensated valve 243The 6th actuator port C with flexible reversal valve 238
Being connected, the first pressure-compensated valve 24 has the control port F through the first pressure-compensated valve 242Flow into hydraulic oil and make the first pressure
The conducting position of force compensating valve 24 conducting, when the first pressure-compensated valve 24 is on, the oil-feed of the first pressure-compensated valve 24
Mouth F1Respectively with the actuator port F of the first pressure-compensated valve 243With oil return opening F4It is connected, wherein, when flexible reversal valve 23 is in
During the first conducting position, the first oil-in C of flexible reversal valve 232With the second actuator port C3Be connected the specially first oil-in
C2With the 5th actuator port C7It is connected, the 6th actuator port C8With the second actuator port C3It is connected；At flexible reversal valve 23
When the second conducting position, the first oil-in C of flexible reversal valve 232With the first actuator port C1Be connected the specially first oil-feed
Mouth C2With the 5th actuator port C7It is connected, the 6th actuator port C8With the first actuator port C1It is connected；
As shown in figure 5 and figure 7, Fig. 7 rises and falls in being the hydraulic control system shown in Fig. 5 reversal valve and the second pressure-compensated valve
Structural representation, the reversal valve 33 that rises and falls also includes the 7th actuator port D7With the 8th actuator port D8, winch control system also wraps
Including the second pressure-compensated valve 34, the second pressure-compensated valve 34 includes oil-in G1, actuator port G3, oil return opening G4With control oil
Mouth G2, the oil-in G of the second pressure-compensated valve 341With control port G2Respectively with the 7th actuator port D of the reversal valve 33 that rises and falls7
It is connected, the actuator port G of the second pressure-compensated valve 343The 8th actuator port D with the reversal valve 33 that rises and falls8Being connected, the second pressure is mended
Repay valve 34 and there is the control port G through the second pressure-compensated valve 342Flow into hydraulic oil and make the second pressure-compensated valve 34 turn on
Conducting position, when the second pressure-compensated valve 34 is on, the oil-in G of the second pressure-compensated valve 341Respectively with second
The actuator port G of pressure-compensated valve 343With oil return opening G4It is connected, wherein, when the reversal valve 33 that rises and falls is in the 3rd conducting position,
Rise and fall the second oil-in D of reversal valve 332With the 3rd actuator port D3Be connected the specially second oil-in D2With the 7th working oil
Mouth D7It is connected, the 8th actuator port D8With the 3rd actuator port D3It is connected；When the reversal valve 33 that rises and falls is in the 4th conducting position
Time, the second oil-in D of the reversal valve 33 that rises and falls2With the 4th actuator port D1Be connected the specially second oil-in D2With the 7th work
Make hydraulic fluid port D7It is connected, the 8th actuator port D8With the 4th actuator port D1It is connected.
Flexible reversal valve 23 in Fig. 6 is three six-way transfer valves, adds the first pressure and mend in telescopic control system
Repay valve 24, continue referring to shown in Fig. 5 and Fig. 6, as a example by contracting arm, when contracting arm control valve 21 turns on, contracting arm control valve 21
The oil that oil-out flows out controls flexible reversal valve 23 and commutates to the first operating position (the i.e. first conducting position), and variable pump 4 provides
Pressure oil is from the first oil-in C2With the 5th actuator port C7Enter to the oil-in F of the first pressure-compensated valve 241And control port
F2, control port F2After oil-feed under oil pressure effect, promote the first pressure-compensated valve 24 to operating position (conducting position), through work
Hydraulic fluid port F3It is back to the 6th actuator port C of flexible reversal valve 238, then through the second actuator port C3Enter rod chamber 11, from without bar
The oil that chamber 12 is flowed out is through the first actuator port C1With the first oil return opening C4Flowing back into hydraulic oil container 8, the retraction completing expansion link is moved
Make.During semi-girder, flexible reversal valve 23 commutates to the second operating position, similar with said process, completes the elongation action of expansion link.
When flexible reversal valve 23 is in middle position, can make in the pipeline that the rod chamber 11 of telescopic oil cylinder 1 is connected with flexible reversal valve 23
Oil is in check valve is back to hydraulic oil container 8, in the pipeline that the rodless cavity 12 of telescopic oil cylinder 1 is connected with flexible reversal valve 23
Oil does not refluxes.
Rising and falling reversal valve 33 can also be for three shown in Fig. 7 six-way transfer valve, operation principle and flexible reversal valve 23
Operation principle is similar to, and repeats the most one by one.
Continuing referring to shown in Fig. 5, in above-mentioned winch control system, winch control system also includes controlling elevator switch
The second shuttle valve 36 and elevator brake valve 10, two oil-ins of the second shuttle valve 36 respectively with the hydraulic fluid port E that hoists of hoist motor 71
With lower oil-falling port E2Being connected, the oil-out of the second shuttle valve 36 is connected with the control port of elevator brake valve 10；
The actuator port of elevator brake valve 10 is connected with the actuator port of the brake 9 of hoist motor.
Second shuttle valve 36 can also substitute with two check valves.
Continuing referring to shown in Fig. 5, in above-mentioned winch control system, winch control system also includes being arranged at elevator horse
Reach the hydraulic fluid port E that hoists of 71With lower oil-falling port E2Between elevator balanced valve 35.
As shown in Figure 5 and Figure 8, Fig. 8 is the structural representation of the elevator balanced valve in the hydraulic control system shown in Fig. 5,
The version of elevator balanced valve 35 has multiple, and elevator balanced valve 35 includes check valve 351 and sequence valve 352, and check valve 351 sets
It is placed in the hydraulic fluid port E that hoists of hoist motor 71Place, two actuator port (H of sequence valve 3521And H2) respectively with the entering of check valve 351
Hydraulic fluid port is connected with oil-out, the guide hydraulic fluid port H of sequence valve 3523Lower oil-falling port E with hoist motor 72It is connected.
In the present embodiment, as a example by elevator falls, when needs suspension hook hoists, hoisting crane control valve 31 controls elevator horse
Reach the hydraulic fluid port E that hoists of 71Turn on system oil-feed oil circuit, the pressure oil of variable pump 4 output the 3rd work by the reversal valve 33 that rises and falls
Make hydraulic fluid port D3Flow to the hydraulic fluid port E that hoists of hoist motor 71, meanwhile, the pressure oil lower oil-falling port E by hoist motor 72Flow direction order
The guide hydraulic fluid port H of valve 3523, the actuator port H of sequence valve 3521Turn on the oil-in of check valve 351, i.e. elevator balanced valve 35
The hydraulic fluid port E that hoists of an actuator port and hoist motor 71Conducting, finally, hoist motor 7 and elevator balanced valve 35 are controlled jointly
Elevator scrolling processed, it is achieved the uniform descent of suspension hook, and then improve the safety of hoisting mechanism action.
Continuing referring to shown in Fig. 5, in above-mentioned hoisting arm expansion control system, hoisting arm expansion control system also includes arranging
Flexible balanced valve 25 between the rodless cavity 12 and rod chamber 11 of telescopic oil cylinder.
As shown in figs. 5 and 9, Fig. 9 is the structural representation of the flexible balanced valve in the hydraulic control system shown in Fig. 5,
The version of flexible balanced valve 25 has multiple, and flexible balanced valve 25 includes bi-bit bi-pass reversal valve 251 and the 3rd damping element
252, bi-bit bi-pass reversal valve 251 includes control port J1With two actuator port (J2And J3), bi-bit bi-pass reversal valve 251
Control port J1It is connected with rod chamber 11 through the 3rd damping element 252,251 two actuator port (J of bi-bit bi-pass reversal valve2With
J3) it is serially connected with the actuator port C of rodless cavity 12 and flexible reversal valve 231Between, bi-bit bi-pass reversal valve 251 has the 5th conducting
Position and the 6th conducting position, when bi-bit bi-pass reversal valve 251 is in the 5th conducting position, two actuator port (J2And J3) unidirectional
Logical, when bi-bit bi-pass reversal valve 251 is in the 6th conducting position, two actuator port (J2And J3) damping conducting, wherein, described
The conducting direction of one-way conduction and damping conducting is contrary.
Two operating positions of the bi-bit bi-pass reversal valve 251 in the flexible balanced valve 25 shown in Fig. 9, an operating position
Use a check valve during conducting, during the conducting of another operating position, use the pipeline with damping.Flexible balanced valve 25 can also wrap
Including a filter, the chip that filter is possible to prevent telescopic oil cylinder to wear and tear enters to hydraulic control system, extends hydraulic control
The service life of system.
The embodiment of the present invention also provides for a kind of hoisting machinery, including the hydraulic control system of any of the above-described kind of hoisting machinery.
Owing to using the hydraulic control system of any of the above-described kind of hoisting machinery in hoisting machinery, it is therefore prevented that stop vertical at contracting arm
I.e. carry out hoisting crane or elevator falls the hoist motor that causes when the operating problem for shortage of oil, and then reduce the event of hoist motor
Barrier rate.
In the present invention, hoisting machinery can be various structures form, such as crawler crane or wheeled crane, is preferably
Wheeled crane, as autocrane.
Obviously, those skilled in the art can carry out various change and the modification essence without deviating from the present invention to the present invention
God and scope.So, if these amendments of the present invention and modification belong to the scope of the claims in the present invention and equivalent technologies thereof
Within, then the present invention is also intended to comprise these change and modification.
Claims (10)
1. a hydraulic control system for hoisting machinery, including: control the hoisting arm expansion control of the telescopic oil cylinder expanding-contracting action of arm
System processed, described hoisting arm expansion control system includes contracting arm control valve and semi-girder control valve；Control hoist motor retractable rope action
Winch control system, described winch control system includes that hoisting crane control valve and elevator fall control valve；Described hoisting arm expansion control
The variable pump that system processed and described winch control system share, for described hoisting arm expansion control system and described rolling control
System fuel feeding, it is characterised in that also include:
Switching valve group, including reversal valve and the first damping element, described reversal valve includes control port, actuator port and oil return
Mouthful, the control port of described reversal valve is connected through the oil-out of described first damping element with described contracting arm control valve, described in change
There is cut-off position and the hydraulic oil that flows into through the control port of described reversal valve and the conducting that makes described reversal valve turn on to valve
Position, when described reversal valve is on, the actuator port of described reversal valve is connected with the oil return opening of described reversal valve；
First shuttle valve, two oil-ins of described first shuttle valve fall with described hoisting crane control valve and elevator the going out of control valve respectively
Hydraulic fluid port is connected, and the oil-out of described first shuttle valve is connected with the actuator port of described reversal valve.
2. hydraulic control system as claimed in claim 1, it is characterised in that described switching valve group also includes the second damping unit
Part, the oil-out of described first shuttle valve is connected with the actuator port of described reversal valve through described second damping element.
3. hydraulic control system as claimed in claim 1, it is characterised in that described hoisting arm expansion control system also includes stretching
Hydraulic control operating valve set, described flexible hydraulic control operating valve set includes flexible reversal valve, described flexible reversal valve include the first oil-in,
Elongation control port, retraction control port, the first actuator port, the second actuator port and the first oil return opening, described flexible commutation
First oil-in of valve is connected with described variable pump, described first actuator port and the second actuator port respectively with described flexible oil
The rodless cavity of cylinder is connected with rod chamber, the elongation control port of described flexible reversal valve and the oil-out phase of described semi-girder control valve
Even, the retraction control port of described flexible reversal valve is connected with the oil-out of described contracting arm control valve, and described flexible reversal valve has
There is the first conducting position making described flexible reversal valve turn on through the hydraulic oil of described retraction control port inflow and through described
Hydraulic oil that elongation control port flows into and make described flexible reversal valve turn on second to turn on position, at described flexible reversal valve
In first conducting position time, the first oil-in of described flexible reversal valve and the second actuator port be connected and the first actuator port and
First oil return opening is connected so that the expansion link of telescopic oil cylinder is retracted, when flexible reversal valve is in the second conducting position, described in stretch
First oil-in of contracting reversal valve and the first actuator port are connected and the second actuator port and the first oil return opening are connected so that
The expansion link elongation of telescopic oil cylinder；
Described winch control system also includes hydraulic control operating valve set of rising and falling, described in hydraulic control operating valve set of rising and falling include commutation of rising and falling
Valve, described in the reversal valve that rises and falls include the second oil-in, lift control hydraulic fluid port, whereabouts control port, the 3rd actuator port, the 4th work
Make hydraulic fluid port and the second oil return opening, described in rise and fall the second oil-in of reversal valve be connected with described variable pump, described 3rd working oil
Mouthful and the 4th actuator port respectively with described hoist motor hoist hydraulic fluid port and lower oil-falling port is connected, described in rise and fall reversal valve
Rise control port to be connected with the oil-out of described hoisting crane control valve, described in rise and fall the whereabouts control port of reversal valve and described volume
Raise control valve oil-out be connected, described in rise and fall reversal valve have through described lift control hydraulic fluid port flow into hydraulic oil and make institute
The 3rd conducting position stating reversal valve conducting of rising and falling and the hydraulic oil flowed into through the control port of described whereabouts and rise and fall described in making and change
To the 4th conducting position of valve conducting, when the described reversal valve that rises and falls is in the 3rd conducting position, described in the second of the reversal valve that rises and falls enter
Hydraulic fluid port and the 3rd actuator port are connected and the 4th actuator port and the second oil return opening are connected so that hoist motor hoists
Action, when the reversal valve that rises and falls is in the 4th conducting position, described in rise and fall the second oil-in of reversal valve and the 4th actuator port phase
Connection and the 3rd actuator port and the second oil return opening are connected so that hoist motor carries out drop action.
4. hydraulic control system as claimed in claim 3, it is characterised in that described flexible reversal valve also includes the 5th working oil
Mouth and the 6th actuator port, described hoisting arm expansion control system also includes the first pressure-compensated valve, described first pressure-compensated valve
Including oil-in, actuator port, oil return opening and control port, the oil-in of described first pressure-compensated valve and control port respectively
It is connected with the 5th actuator port of described flexible reversal valve, the actuator port of described first pressure-compensated valve and described flexible commutation
6th actuator port of valve is connected, and the control port that described first pressure-compensated valve has through described first pressure-compensated valve flows into
Hydraulic oil and make the conducting position of described first pressure-compensated valve conducting, when described first pressure-compensated valve is on,
The oil-in of described first pressure-compensated valve is connected with actuator port and the oil return opening of described first pressure-compensated valve respectively, its
In, when described flexible reversal valve is in the first conducting position, the first oil-in of described flexible reversal valve and the second actuator port
Being connected the specially first oil-in and the 5th actuator port is connected, the 6th actuator port and the second actuator port are connected；
When described flexible reversal valve is in the second conducting position, the first oil-in of described flexible reversal valve and the first actuator port are connected
Logical specially the first oil-in and the 5th actuator port are connected, and the 6th actuator port and the first actuator port are connected；
The described reversal valve that rises and falls also includes that the 7th actuator port and the 8th actuator port, described winch control system also include second
Pressure-compensated valve, described second pressure-compensated valve includes oil-in, actuator port, oil return opening and control port, described second pressure
The oil-in of force compensating valve with control port respectively the 7th actuator port with the described reversal valve that rises and falls be connected, described second pressure
The actuator port of recuperation valve is connected with the 8th actuator port of the described reversal valve that rises and falls, and described second pressure-compensated valve has through institute
State the hydraulic oil of the control port inflow of the second pressure-compensated valve and make the conducting position of described second pressure-compensated valve conducting, work as institute
State the second pressure-compensated valve when being on, the oil-in of described second pressure-compensated valve respectively with described second pressure compensation
The actuator port of valve is connected with oil return opening, wherein, when the described reversal valve that rises and falls is in the 3rd conducting position, described in rise and fall commutation
Second oil-in of valve and the 3rd actuator port are connected the specially second oil-in and the 7th actuator port is connected, the 8th work
Make hydraulic fluid port and the 3rd actuator port is connected；When the described reversal valve that rises and falls is in the 4th conducting position, described in rise and fall reversal valve
Second oil-in and the 4th actuator port are connected the specially second oil-in and the 7th actuator port is connected, the 8th working oil
Mouth is connected with the 4th actuator port.
5. hydraulic control system as claimed in claim 1, it is characterised in that described winch control system also includes controlling elevator
Second shuttle valve of switch and elevator brake valve, two oil-ins of described second shuttle valve respectively with the oil that hoists of described hoist motor
Mouth is connected with lower oil-falling port, and the oil-out of described second shuttle valve is connected with the control port of described elevator brake valve；
The actuator port of described elevator brake valve is connected with the actuator port of the brake of described hoist motor.
6. hydraulic control system as claimed in claim 1, it is characterised in that described winch control system also includes being arranged at institute
State the elevator balanced valve hoisted between hydraulic fluid port and lower oil-falling port of hoist motor.
7. hydraulic control system as claimed in claim 6, it is characterised in that described elevator balanced valve includes check valve and order
Valve, described check valve is arranged at the oil port that hoists of described hoist motor, two actuator ports of described sequence valve respectively with institute
The oil-in stating check valve is connected with oil-out, the lower oil-falling port phase of guide's hydraulic fluid port of described sequence valve and described hoist motor
Even.
8. hydraulic control system as claimed in claim 1, it is characterised in that described hoisting arm expansion control system also includes arranging
Flexible balanced valve between the rodless cavity and rod chamber of described telescopic oil cylinder.
9. hydraulic control system as claimed in claim 8, it is characterised in that described flexible balanced valve includes that bi-bit bi-pass commutates
Valve and the 3rd damping element, described bi-bit bi-pass reversal valve includes control port and two actuator ports, and described bi-bit bi-pass changes
It is connected with described rod chamber through described 3rd damping element to the control port of valve, two work of described bi-bit bi-pass reversal valve
Hydraulic fluid port is serially connected with between the actuator port of described rodless cavity and described flexible reversal valve, and described bi-bit bi-pass reversal valve has the 5th
Conducting position and the 6th conducting position, when described bi-bit bi-pass reversal valve is in the 5th conducting position, two actuator port one-way conductions,
When described bi-bit bi-pass reversal valve is in the 6th conducting position, the damping conducting of two actuator ports, wherein, described one-way conduction and
The conducting direction of damping conducting is contrary.
10. a hoisting machinery, it is characterised in that include the hydraulic pressure control of hoisting machinery as described in any one of claim 1～9
System processed.
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| CN106256751B (en) * | 2015-06-17 | 2017-10-27 | 徐工集团工程机械股份有限公司 | The control method and system and crane of single-cylinder bolt type telescopic boom arm pin back-off |
| CN106006416B (en) * | 2016-07-07 | 2018-06-26 | 徐州重型机械有限公司 | Fix the stepless luffing device of auxiliary and crane |
| CN108223629B (en) * | 2018-03-23 | 2019-05-03 | 中国十七冶集团有限公司 | Hydraulic gyration part from moving constraint control device |
| CN108298441A (en) * | 2018-03-30 | 2018-07-20 | 安徽柳工起重机有限公司 | The control method and dedicated control system of crane stretch |
| CN108275595B (en) * | 2018-03-30 | 2024-07-02 | 安徽柳工起重机有限公司 | Hoist control system of crane super-lift mechanism and crane super-lift mechanism |
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| SU1359247A1 (en) * | 1986-06-30 | 1987-12-15 | Московское научно-производственное объединение по строительному и дорожному машиностроению | Boom crane hydraulic drive |
| CN2652902Y (en) * | 2003-09-16 | 2004-11-03 | 江苏省机电研究所有限公司 | Hydraulic crane control system |
| CN101229902A (en) * | 2008-02-19 | 2008-07-30 | 湖南三一起重机械有限公司 | Hydraulic oil distribution controlling device for crane hydraulic system |
| CN102979778A (en) * | 2012-12-07 | 2013-03-20 | 中联重科股份有限公司 | Three-position six-way reversing valve, hydraulic control system and engineering vehicle |
| CN203130636U (en) * | 2013-01-15 | 2013-08-14 | 中联重科股份有限公司 | Engineering mechanical equipment and hydraulic control loop thereof |
| CN203754318U (en) * | 2014-02-26 | 2014-08-06 | 中联重科股份有限公司 | Crane hoisting hydraulic system and crane |
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| CN104444816A (en) | 2015-03-25 |
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