CN106698199A - Double-derricking cylinder hydraulic control system - Google Patents
Double-derricking cylinder hydraulic control system Download PDFInfo
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- CN106698199A CN106698199A CN201710057158.6A CN201710057158A CN106698199A CN 106698199 A CN106698199 A CN 106698199A CN 201710057158 A CN201710057158 A CN 201710057158A CN 106698199 A CN106698199 A CN 106698199A
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- 230000001360 synchronised effect Effects 0.000 claims abstract 4
- 239000012530 fluid Substances 0.000 claims description 48
- 230000008929 regeneration Effects 0.000 claims description 15
- 238000011069 regeneration method Methods 0.000 claims description 15
- 239000002828 fuel tank Substances 0.000 claims description 11
- 238000004891 communication Methods 0.000 claims description 5
- 238000006073 displacement reaction Methods 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 180
- 239000010720 hydraulic oil Substances 0.000 description 26
- 230000007423 decrease Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 239000000725 suspension Substances 0.000 description 4
- 230000001172 regenerating effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000005381 potential energy Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
-
- 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
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C2700/00—Cranes
- B66C2700/03—Cranes with arms or jibs; Multiple cranes
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- Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Mechanical Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a double-derricking cylinder hydraulic control system. The double-derricking cylinder hydraulic control system further comprises a two-position three-way reversing valve, a cartridge valve and a synchronous control device; a port A of a three-position four-way reversing valve communicates with a first working oil port of the cartridge valve; a control oil port of the cartridge valve communicates with a port A of the two-position three-way reversing valve; a port B of the two-position three-way reversing valve communicates with a second working oil port of the cartridge valve; the second working oil port of the cartridge valve communicates with a first oil port of the synchronous control device; a second oil port of the synchronous control device communicates with rodless cavities of a first derricking cylinder and a second derricking cylinder; and rod cavities of the first derricking cylinder and the second derricking cylinder communicate with a port B of the three-position four-way reversing valve. The double-derricking cylinder hydraulic control system realizes the locking function through the two-position three-way reversing valve and the cartridge valve, and prevents shaking of a lifting arm.
Description
Technical field
The present invention relates to crane field, more particularly to a kind of pair amplitude oil cylinder hydraulic control system.
Background technology
The flexible luffing angle to change arm that the arm of crane passes through amplitude oil cylinder, with completing the course of work
Arm raising or decline.The arm of goliath typically uses double amplitude oil cylinders, i.e., using two amplitude oil cylinder simultaneous retractables
Luffing to realize arm is acted.This requires that two amplitude oil cylinders will keep good synchronism in the course of the work.
For double amplitude oil cylinders, generally realized using three position four-way directional control valve, balanced valve, flow divider to double luffings at present
The control of oil cylinder.Wherein, A mouthfuls of three position four-way directional control valve is connected with the oil inlet of balanced valve, oil-out and the shunting of balanced valve
The oil inlet connection of valve, the rod chamber of the pilot control hydraulic fluid port of balanced valve respectively with two amplitude oil cylinders is connected, and the two of flow divider
Rodless cavity of the individual oil-out respectively with two amplitude oil cylinders is connected, and two rod chambers of amplitude oil cylinder commutate with 3-position 4-way respectively
Oil-feed B mouthfuls of connection of valve.
Realize it is of the invention during, inventor find prior art at least there is problems with：
Arm is in the course of the work, it may be desirable to which it is motionless to be maintained at a certain angle, is generally protected using balanced valve now
Arm This move is held, specifically, the valve element of balanced valve closes the hydraulic oil locked in two rodless cavities of amplitude oil cylinder, so that
It is parked in two amplitude oil cylinders arbitrarily angled motionless, but during arm decline, the telescopic end of amplitude oil cylinder is retracted, now
Need to open balanced valve by arm decline, balanced valve is the opened by pressure by its pilot control oil port hydraulic oil, while
During declining in arm, load passes to two power of amplitude oil cylinder by arm can be with the change of boom angle
It is continually changing, because the stress of two amplitude oil cylinders is continually changing so that the hydraulic oil pressure in two rod chambers of amplitude oil cylinder
Power is continually changing, and because the rod chamber of the pilot control hydraulic fluid port respectively with two amplitude oil cylinders of balanced valve is connected, this can cause to put down
Hydraulic fluid pressure at the pilot control opening of valve that weighs also is continually changing, and the hydraulic fluid pressure at the pilot control opening of balanced valve is not
Disconnected change, the hydraulic fluid pressure being continually changing make to flow into two luffing oil by balanced valve so that the valve element of balanced valve is unstable
The hydraulic oil generation pressure fluctuation of the rodless cavity of cylinder, pressure fluctuation can make the movement velocity of the piston rod of amplitude oil cylinder uneven,
So as to cause jitter phenomenon of the arm during decline, the security of crane is reduced.
The content of the invention
In order to solve the problems, such as that arm has jitter phenomenon during decline in the prior art, the embodiment of the present invention is provided
A kind of pair of amplitude oil cylinder hydraulic control system.The technical scheme is as follows：
The embodiment of the invention provides a kind of pair of amplitude oil cylinder hydraulic control system, it is adaptable to control the first amplitude oil cylinder and
Second amplitude oil cylinder, described pair of amplitude oil cylinder hydraulic control system includes：Three position four-way directional control valve, described pair of amplitude oil cylinder hydraulic pressure
Control system also includes：Two-bit triplet reversal valve, inserted valve and sync control device, A mouthfuls of the three position four-way directional control valve with
The first actuator port connection of the inserted valve, the control port of the inserted valve connects with A mouthfuls of the two-bit triplet reversal valve
Logical, B mouthfuls of the two-bit triplet reversal valve connects with the second actuator port of the inserted valve, the two-bit triplet reversal valve
C mouthfuls is connected with fuel tank, and the second actuator port of the inserted valve is also connected with the first hydraulic fluid port of the sync control device, described
Second hydraulic fluid port of sync control device is respectively with the rodless cavity of first amplitude oil cylinder and second amplitude oil cylinder without bar
Chamber connects, and the rod chamber of the rod chamber of first amplitude oil cylinder and second amplitude oil cylinder commutates with the 3-position 4-way
B mouthfuls of connection of valve.
Specifically, A mouthfuls of the three position four-way directional control valve of the first working position and the T mouths of the three position four-way directional control valve
Between oil circuit on offer first segment discharge orifice.
Specifically, described pair of amplitude oil cylinder hydraulic control system also includes：Regeneration check valve, the regeneration check valve enters
Oil communication between A mouthfuls of hydraulic fluid port and the three position four-way directional control valve and T mouthfuls, and the oil inlet arrangement for regenerating check valve
At A mouthfuls of the three position four-way directional control valve and the first segment discharge orifice between, the oil-out and described three of the regeneration check valve
Oil communication between B mouthfuls of position and four-way reversing valve and P mouthfuls.
Further, P mouthfuls of B mouthfuls of the three position four-way directional control valve of the first working position and the three position four-way directional control valve
Between oil circuit on offer the second throttle orifice, and second throttle orifice is arranged in oil-out and the institute of the regeneration check valve
State between B mouthfuls of three position four-way directional control valve.
Specifically, described pair of amplitude oil cylinder hydraulic control system also includes：Pressure limiting valve, the oil inlet of the pressure limiting valve and institute
The first hydraulic fluid port connection of sync control device is stated, the oil-out of the pressure limiting valve is connected with fuel tank, and pressure limiting valve setting
Pressure value is less than or equal to first amplitude oil cylinder or the rated operating pressure value of second amplitude oil cylinder.
Further, described pair of amplitude oil cylinder hydraulic control system also includes：Repairing check valve, the repairing check valve
Oil inlet is connected with the oil inlet of the pressure limiting valve, and the oil-out of the repairing check valve connects with the oil-out of the pressure limiting valve
It is logical.
Specifically, the three position four-way directional control valve is hydraulic control pilot-operated type three position four-way directional control valve, the two-bit triplet commutation
Valve is hydraulic control pilot-operated type two-bit triplet reversal valve, and described pair of amplitude oil cylinder hydraulic control system also includes：Pilot-actuated valve, it is described
Pilot-actuated valve includes the first three-way pressure reducing valve and the second three-way pressure reducing valve, the oil-out of first three-way pressure reducing valve respectively with
D mouthfuls of the two-bit triplet reversal valve is connected with the first pilot control hydraulic fluid port of the hydraulic control pilot-operated type three position four-way directional control valve,
The oil-out of second three-way pressure reducing valve connects with the second pilot control hydraulic fluid port of the hydraulic control pilot-operated type three position four-way directional control valve
It is logical.
Further, the sync control device includes syncmotor, and the syncmotor includes：Coaxially connected first
Two-way quantitative motor and the second two-way quantitative motor, the second actuator port of the inserted valve respectively with first two-way quantitative
First hydraulic fluid port of motor is connected with the first hydraulic fluid port of the second two-way quantitative motor, and the second of the first two-way quantitative motor
Hydraulic fluid port is connected with the rodless cavity of first amplitude oil cylinder, and the second hydraulic fluid port of the second two-way quantitative motor becomes with described second
The rodless cavity connection of width oil cylinder.
Further, the first oil of the first hydraulic fluid port of the first two-way quantitative motor and the second two-way quantitative motor
Connected with the second actuator port of the inserted valve again after mouth connection.
Further, between A mouthfuls and T mouthfuls of the three position four-way directional control valve of the three position four-way directional control valve of middle position
The 3rd throttle orifice is offered on oil circuit.
Further, between B mouthfuls and T mouthfuls of the three position four-way directional control valve of the three position four-way directional control valve of middle position
The 4th throttle orifice is offered on oil circuit.
The beneficial effect that technical scheme provided in an embodiment of the present invention is brought is：The invention provides a kind of pair of amplitude oil cylinder
Hydraulic control system, is realized to the first amplitude oil cylinder and the lock of the second amplitude oil cylinder by two-bit triplet reversal valve and inserted valve
Tightly, because the valve element of inserted valve is to control whether inserted valve is turned on and off by the logical oily mode of control port, control port
Hydraulic fluid pressure can't have an impact to the valve element aperture of inserted valve, this causes that the unlatching of inserted valve will not be subject to hydraulic oil pressure
The influence of power, so as to avoid the situation that double amplitude oil cylinder hydraulic control systems are shaken in the locked condition.
Brief description of the drawings
Technical scheme in order to illustrate more clearly the embodiments of the present invention, below will be to that will make needed for embodiment description
Accompanying drawing is briefly described, it should be apparent that, drawings in the following description are only some embodiments of the present invention, for
For those of ordinary skill in the art, on the premise of not paying creative work, other can also be obtained according to these accompanying drawings
Accompanying drawing.
Fig. 1 is the provided in an embodiment of the present invention pair of schematic diagram of amplitude oil cylinder hydraulic control system；
Fig. 2 is the schematic diagram of three position four-way directional control valve provided in an embodiment of the present invention；
Fig. 3 is the principle that provided in an embodiment of the present invention pair of amplitude oil cylinder hydraulic control system suspension arm variable-amplitude keeps operating mode
Figure.
Specific embodiment
To make the object, technical solutions and advantages of the present invention clearer, below in conjunction with accompanying drawing to embodiment party of the present invention
Formula is described in further detail.
Embodiment
The embodiment of the invention provides a kind of pair of amplitude oil cylinder hydraulic control system, it is adaptable to the double amplitude oil cylinders of control,
In the present embodiment, this pair of amplitude oil cylinder includes the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1.Fig. 1 is provided for the embodiment of the present invention
Double amplitude oil cylinder hydraulic control systems schematic diagram.As shown in figure 1, this pair of amplitude oil cylinder hydraulic control system includes：Three
Four-way reversing valve 3, two-bit triplet reversal valve 4, inserted valve 5 and sync control device 7.
A mouthfuls of three position four-way directional control valve 3 connects with the first actuator port of inserted valve 5, the control port of inserted valve 5 and two
A mouthfuls of connection of position three-way diverter valve 4, B mouthfuls of two-bit triplet reversal valve 4 connects with the second actuator port of inserted valve 5.Two three
C mouthfuls of logical reversal valve 4 is connected with fuel tank 14.Inserted valve 5 the second actuator port mouth also with the first hydraulic fluid port of sync control device 7
Connection.Second hydraulic fluid port of sync control device 7 respectively with the rodless cavity 2a and the nothing of the second amplitude oil cylinder 1 of the first amplitude oil cylinder 2
Rod cavity 1a is connected.The rod chamber 1b of the rod chamber 2b of the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1 is and three position four-way directional control valve
3 B mouthfuls of connection.The oil-out of pilot-actuated valve 6 is connected with commutation D mouthfuls of two-bit triplet reversal valve 4.
Wherein, three position four-way directional control valve 3 also includes P mouthfuls, and P mouthfuls is the oil inlet of three position four-way directional control valve 3, can be with system
Hydraulic oil oil-feed port connection, T mouthful be three position four-way directional control valve 3 oil return opening, can be connected with the oil return opening of system, generally
T mouthfuls connects with fuel tank.
Fig. 2 is the schematic diagram of three position four-way directional control valve provided in an embodiment of the present invention 3.As shown in Fig. 2 three four of left position
First segment discharge orifice 11 is offered on oil circuit between A mouthfuls and T mouthfuls of three position four-way directional control valve 3 of logical reversal valve 3.By opening up
One throttle orifice 11 can improve the return pressure of oil circuit where it, and first segment discharge orifice 11 is prevented from arm and is sent out because conducting oneself with dignity larger
The situation of drop stall is given birth to, so as to realize the function of speed limit, it is ensured that the normal work of arm, is realized by first segment discharge orifice 11
During speed limiting function, first segment discharge orifice 11 will not be influenceed by hydraulic fluid pressure, so as to avoid asking for arm shake
Topic.
Due to inserted valve 5 valve element be tapered valve element so that inserted valve 5 the second actuator port along inserted valve 5 radial direction
Direction is equivalent hydraulic fluid port so that oil circuit can be connected nearby, reduces the volume of double amplitude oil cylinder hydraulic control systems.Wherein,
At A mouths in the first actuator port such as Fig. 1, inserted valve 5 is at B mouths in the second actuator port such as Fig. 1 for inserted valve 5.
First amplitude oil cylinder 2 and the second amplitude oil cylinder 1 are two-action single-rod hydraulic cylinder, and the first amplitude oil cylinder 2
Performance parameter with the second amplitude oil cylinder 1 is consistent.In the present embodiment, three position four-way directional control valve 3 is that Median Function is the three of Y types
Position and four-way reversing valve, meanwhile, three position four-way directional control valve 3 has function, the first working position of three position four-way directional control valve 3 in automatic returning
The side working position that the internal oil passages of three position four-way directional control valve 3 intersect is referred to, i.e. P mouthfuls connects with B mouthfuls, and T mouthfuls connects with A mouthfuls；
The middle position of three position four-way directional control valve 3 refers to that T mouthfuls connects with A mouthfuls and B mouthfuls respectively, what the second working position of three position four-way directional control valve 3 referred to
It is the parallel side working position of the internal oil passages of three position four-way directional control valve 3, i.e. P mouthfuls connects with A mouthfuls, T mouthfuls connects with B mouthfuls.
Specifically, sync control device 7 can include syncmotor, and syncmotor includes：Coaxially connected first is two-way
Fixed displacement motor 7a and the second two-way quantitative motor 7b, the second actuator port of inserted valve 5 respectively with the first two-way quantitative motor 7a
The first hydraulic fluid port and the second two-way quantitative motor 7b the connection of the first hydraulic fluid port, second hydraulic fluid port of the first two-way quantitative motor 7a and the
The rodless cavity 2a connections of one amplitude oil cylinder 2, second hydraulic fluid port of the second two-way quantitative motor 7b and the rodless cavity of the second amplitude oil cylinder 1
1a is connected.The luffing angle change of arm (not shown) arm in amplitude changing process, this can cause stretching for the first amplitude oil cylinder 2
The stress of the telescopic end of contracting end and the second amplitude oil cylinder 1 is continually changing, and along with reasons such as the assembling of arm and mismachining tolerances, makes
The stress for obtaining the telescopic end of the telescopic end and the second amplitude oil cylinder 1 of the first amplitude oil cylinder 2 is inconsistent, in order to avoid the first luffing oil
The situation that the flow of the hydraulic oil being passed through in the rodless cavity 1a of the rodless cavity 2a of cylinder 2 and the second amplitude oil cylinder 1 is inconsistent occurs,
In the present embodiment, make the performance parameter of the first two-way quantitative motor 7a and the second two-way quantitative motor 7b consistent, specifically, make the
One two-way fixed displacement motor 7a and the second two-way quantitative motor 7b discharge capacities are completely the same.So ensure that the first two-way quantitative motor
The output flow of 7a and the second two-way quantitative motor 7b is consistent, so as to ensure that the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1 exist
The synchronism that luffing is acted when declining.Syncmotor is that this is caused together by a rigidly connected two two-way quantitative motor of axle
Step motor exactly can be equally distributed hydraulic oil to the rodless cavity 2a and the second amplitude oil cylinder 1 of the first amplitude oil cylinder 2
In rodless cavity 1a, so as to ensure that the synchronism of the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1, and then double luffing oil are ensure that
The control accuracy of cylinder hydraulic control system.In other embodiments, the sync control device 7 can also be for proportioning valve (in figure not
Show) etc..
Further, first hydraulic fluid port of first hydraulic fluid port of the first two-way quantitative motor 7a and the second two-way quantitative motor 7b can
Connected with the second actuator port after connection again with inserted valve 5.So setting can simplify oil circuit, and reduce double amplitude oil cylinder liquid
The volume and reduction processing cost of pressure control system.
Specifically, this pair of amplitude oil cylinder hydraulic control system can also include：Pressure limiting valve 8, the oil inlet of pressure limiting valve 8 with it is same
The first hydraulic fluid port connection of control device 7 is walked, the oil-out of pressure limiting valve 8 is connected with fuel tank, and the pressure value of the setting of pressure limiting valve 8 is less than
Or equal to the first amplitude oil cylinder 2 or the rated operating pressure value of the second amplitude oil cylinder 1.Wherein, the first amplitude oil cylinder 2 or second becomes
The rated operating pressure value of width oil cylinder 1 refers to the pressure of the first amplitude oil cylinder 2 or the energy of the second amplitude oil cylinder 1 normal work steady in a long-term
Power.During suspension arm variable-amplitude action keeps, the rodless cavity 1a of the rodless cavity 2a of the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1
Interior hydraulic oil is populated valve 5 and locks, and realizes the effect of support arm, sets the nothing that pressure limiting valve 8 is prevented from the first amplitude oil cylinder 2
Hydraulic fluid pressure in the rodless cavity 1a of rod cavity 2a and the second amplitude oil cylinder 1 is too high, influences the first amplitude oil cylinder 2 and the second luffing
The normal of oil cylinder 1 is used, and when hydraulic fluid pressure is too high, section hydraulic oil is flowed into fuel tank by pressure limiting valve 8.
Further, this pair of amplitude oil cylinder hydraulic control system can also include：Repairing check valve 9, repairing check valve 9
Oil inlet is connected with the oil inlet of pressure limiting valve 8, and the oil-out of repairing check valve 9 is connected with the oil-out of pressure limiting valve 8.When arm is needed
When wanting rapid increase, the piston rod of the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1 needs quickly to stretch out, the hydraulic oil in system
Traffic requirement can not be met, now can by rodless cavity 2a from repairing check valve 9 to the first amplitude oil cylinder 2 and the second amplitude oil cylinder
Repairing in 1 rodless cavity 1a, will hydraulic oil be passed through by the oil inlet of repairing check valve 9 so that hydraulic oil can be by repairing list
Flowed into valve 9 in the rodless cavity 2a of the first amplitude oil cylinder 2 and the rodless cavity 1a of the second amplitude oil cylinder 1, so as to ensure the first luffing
Hydraulic oil in the rodless cavity 1a of the rodless cavity 2a of oil cylinder 2 and the second amplitude oil cylinder 1 has certain pressure, for preventing arm
There is the situation that hypervelocity is emptied when luffing declines.
Specifically, three position four-way directional control valve 3 can be hydraulic control pilot-operated type three position four-way directional control valve.Two-bit triplet reversal valve 4
It is hydraulic control pilot-operated type two-bit triplet reversal valve, double amplitude oil cylinder hydraulic control systems also include：Pilot-actuated valve 6, pilot control
Valve 6 can include the first three-way pressure reducing valve 6a and the second three-way pressure reducing valve 6b, the first three-way pressure reducing valve 6a oil-out respectively with
D mouthfuls of two-bit triplet reversal valve 4 is connected with the first pilot control hydraulic fluid port f of hydraulic control pilot-operated type three position four-way directional control valve, and the two or three
The oil-out of logical pressure-reducing valve 6b is connected with the second pilot control hydraulic fluid port g of hydraulic control pilot-operated type three position four-way directional control valve.First threeway
Oil-feed P mouthfuls of pressure-reducing valve 6a and oil-feed P mouthfuls of the second three-way pressure reducing valve 6b connects with the pilot control oil-feed port of system respectively.The
Oil return T mouthfuls of one three-way pressure reducing valve 6a and oil return T mouthfuls of the second three-way pressure reducing valve 6b are connected with the oil return opening of system respectively.At this
In embodiment, oil-feed P mouthfuls of the first three-way pressure reducing valve 6a and oil-feed P mouthfuls of the second three-way pressure reducing valve 6b can first connect after again with
The pilot control oil-feed port connection of system, oil return T mouthfuls of the first three-way pressure reducing valve 6a and oil return T mouthfuls of the second three-way pressure reducing valve 6b
Oil return opening after can first connecting again with system is connected.In other embodiments, the pilot-actuated valve 6 can also be electromagnetic switch
Valve (not shown).In the present embodiment, three position four-way directional control valve 3 is that Median Function is the hydraulic control pilot-operated type 3-position 4-way of Y types
Reversal valve, meanwhile, three position four-way directional control valve 3 has function in automatic returning.In other embodiments, the three position four-way directional control valve 3
It can be electromagnetic switch three position four-way directional control valve (not shown).In other embodiments, two-bit triplet reversal valve 4 can be electricity
Magnetic commutation two-bit triplet reversal valve (not shown).
Specifically, as shown in Fig. 2 this pair of amplitude oil cylinder hydraulic control system can also include：Regeneration check valve 10, regeneration
Oil communication between the oil inlet of check valve 10 and A mouthfuls of three position four-way directional control valve 3 and T mouthfuls, and regenerate entering for check valve 10
Hydraulic fluid port is arranged between the A of three position four-way directional control valve 3 mouthfuls and first segment discharge orifice 11, regenerate check valve 10 oil-out and three four
Oil communication between B mouthfuls and P mouthfuls of logical reversal valve 3.After first segment discharge orifice 11 improves return pressure, a part of oil return
Hydraulic oil is flowed into by regeneration check valve 10, and flow to the rod chamber 2b of the first amplitude oil cylinder 2 and the rod chamber of the second amplitude oil cylinder 1
In 1b.When the telescopic end of the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1 is retracted (arm decline), by regenerating check valve 10
By the potential energy of arm into hydraulic energy, double amplitude oil cylinder hydraulic control system heating temps are reduced, while accelerate hang again
The speed that arm luffing declines, improves the operating efficiency of arm.In practice, regeneration check valve 10 can commutate with 3-position 4-way
Valve 3 is integrated on a valve block, so as to reduce the volume of double amplitude oil cylinder hydraulic control systems.
Further, between B mouthfuls and P mouthfuls of three position four-way directional control valve 3 of the three position four-way directional control valve 3 of the first working position
Offer the second throttle orifice 12 on oil circuit, and the second throttle orifice 12 is arranged in the oil-out of regeneration check valve 10 and is changed with 3-position 4-way
Between A mouthfuls of valve 3.Second throttle orifice 12 can improve the pressure of oil circuit where it, it is ensured that be flowed out by regeneration check valve 10
Most of hydraulic oil can be flowed into the rod chamber 2b of the first amplitude oil cylinder 2 and the rod chamber 1b of the second amplitude oil cylinder 1.Meanwhile,
When the pressure that second throttle orifice 12 improves oil circuit where it can avoid arm from carrying load in stall conditions, hydraulic oil can not
It is passed through in the rod chamber 1b of the rod chamber 2b of the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1 in time.Three four of first working position
The second throttle orifice 12 is offered on oil circuit between B mouthfuls and P mouthfuls of three position four-way directional control valve 3 of logical reversal valve 3
Specifically, opened on the oil circuit between A mouthfuls and T mouthfuls of three position four-way directional control valve 3 of the three position four-way directional control valve 3 of middle position
The 3rd throttle orifice 15 is provided with, on the oil circuit between B mouthfuls and T mouthfuls of three position four-way directional control valve 3 of the three position four-way directional control valve 3 of middle position
Offer the 4th throttle orifice 16.3rd throttle orifice 15 and the 4th throttle orifice 16 can be the 3rd throttle orifice 15 and the 4th throttle orifice 16
The oil circuit at place increases resistance, prevents hydraulic oil from quickly flowing back to fuel tank, makes the derricking speed of arm too fast, influences the peace of crane
Quan Xing.Wherein, the middle position of three position four-way directional control valve 3 refers to that T mouthfuls connects with A mouthfuls and B mouthfuls respectively.
Following is a brief introduction of the provided in an embodiment of the present invention pair of operation principle of amplitude oil cylinder hydraulic control system：
Arm declines process：Three position four-way directional control valve 3 commutates, and three position four-way directional control valve 3 is in the first working position, referring to
Fig. 1, now, P mouthfuls of three position four-way directional control valve 3 is connected with B mouthfuls, and A mouthfuls of three position four-way directional control valve 3 is connected with T mouthfuls, hydraulic oil by
P mouthfuls of inflow of three position four-way directional control valve 3, and by B mouthfuls of outflow of three position four-way directional control valve 3, then separately flow into the first amplitude oil cylinder 2
Rod chamber 2b and the second amplitude oil cylinder 1 rod chamber 1b in, the telescopic end of the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1
Telescopic end is retracted, and realizes that arm declines, in the rodless cavity 1a of the rodless cavity 2a of the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1
Hydraulic oil the second actuator port of inserted valve 5 is flow to by sync control device 7, two-bit triplet reversal valve 4 is in first
Working position (upper working position in Fig. 1), now, the control port of inserted valve 5 is connected with fuel tank 14, in the first work of inserted valve 5
Under the pressure effect of hydraulic fluid port hydraulic oil, the valve element of inserted valve 5 overcomes the spring force that its spring cavity inner spring is provided to be unlocked, hydraulic pressure
Oil is flow to the first actuator port of inserted valve 5 by the second actuator port of inserted valve 5, and by A mouthfuls of stream of three position four-way directional control valve 3
To T mouthfuls of cocurrent oil return box of three position four-way directional control valve 3.
Suspension arm variable-amplitude acts holding process：Fig. 3 hangs for provided in an embodiment of the present invention pair of amplitude oil cylinder hydraulic control system
Arm luffing keeps the schematic diagram of operating mode.As shown in figure 3, three position four-way directional control valve 3 is in middle position, P mouthfuls of three position four-way directional control valve 3
It is cut off, T mouthfuls of three position four-way directional control valve 3 is connected with A mouthfuls and B mouthfuls respectively so that two-bit triplet reversal valve 4 is provided in its spring
Spring-force driven dual under in the second working position (in Fig. 1 lower working position), now, control port and the inserted valve 5 of inserted valve 5
First actuator port is connected, under the collective effect of the spring force of inserted valve 5 and the pressure of control oil, the valve element of inserted valve 5 is tight
It is pressed on the valve seat of inserted valve 5, prevents hydraulic oil from the first work of inserted valve 5 is leaked to by the second actuator port of inserted valve 5
Hydraulic fluid port, makes the hydraulic fluid port of the rodless cavity 1a of the rodless cavity 2a of the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1 locked, the first luffing
The amplitude oil cylinder 1 of oil cylinder 2 and second realizes the supporting role to arm, makes arm keep its luffing angle constant.
Arm raising process：Three position four-way directional control valve 3 commutates, and three position four-way directional control valve 3 is in the second working position, this
When, P mouthfuls of three position four-way directional control valve 3 is connected with A mouthfuls, and B mouthfuls of three position four-way directional control valve 3 is connected with T mouthfuls, and hydraulic oil is by three four
P mouthfuls of inflow of logical reversal valve 3, and by A mouthfuls of outflow of three position four-way directional control valve 3, flow at the first actuator port of inserted valve 5,
Two-bit triplet reversal valve 4 is set to be in the first working position, now, the control port of inserted valve 5 is connected with fuel tank 14, then inserted valve 5
Valve element inserted valve 5 the first actuator port hydraulic oil pressure effect under be unlocked, hydraulic oil by inserted valve 5 the first work
The second actuator port of inserted valve 5 is flow to as hydraulic fluid port, by sync control device 7 separately flow into the first amplitude oil cylinder 2 without bar
In the rodless cavity 1a of chamber 2a and the second amplitude oil cylinder 1, the telescopic end of the telescopic end of the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1
Stretch out, realize suspension arm variable-amplitude raising, in the rod chamber 1b of the rod chamber 2b of the first amplitude oil cylinder 2 and the second amplitude oil cylinder 1
The T mouthfuls of cocurrent oil return box that hydraulic oil flow to three position four-way directional control valve 3 by B mouthfuls of three position four-way directional control valve 3.
The invention provides a kind of pair of amplitude oil cylinder hydraulic control system, realized by two-bit triplet reversal valve and inserted valve
Locking to the first amplitude oil cylinder and the second amplitude oil cylinder, because inserted valve is to control inserting by the logical oily mode of control port
Whether valve is turned on and off, and the hydraulic fluid pressure of control port can't have an impact to the valve element aperture of inserted valve, and this causes to insert
The valve element for filling valve is opened and will not influenceed by hydraulic fluid pressure, so as to avoid double amplitude oil cylinder hydraulic control systems in locking
Situation about being shaken under state.
The foregoing is only presently preferred embodiments of the present invention, be not intended to limit the invention, it is all it is of the invention spirit and
Within principle, any modification, equivalent substitution and improvements made etc. should be included within the scope of the present invention.
Claims (10)
1. a kind of pair of amplitude oil cylinder hydraulic control system, it is adaptable to control the first amplitude oil cylinder and the second amplitude oil cylinder, it is described double
Amplitude oil cylinder hydraulic control system includes：Three position four-way directional control valve, it is characterised in that described pair of amplitude oil cylinder hydraulic control system
Also include：Two-bit triplet reversal valve, inserted valve and sync control device, A mouthfuls of the three position four-way directional control valve with the inserting
The first actuator port connection of valve, the control port of the inserted valve is connected with A mouthfuls of the two-bit triplet reversal valve, and described two
B mouthfuls of three-way diverter valve of position connects with the second actuator port of the inserted valve, C mouthfuls and fuel tank of the two-bit triplet reversal valve
Connection, the second actuator port of the inserted valve is also connected with the first hydraulic fluid port of the sync control device, the Synchronization Control
Second hydraulic fluid port of device is connected with the rodless cavity of first amplitude oil cylinder and the rodless cavity of second amplitude oil cylinder respectively, institute
State the first amplitude oil cylinder rod chamber and second amplitude oil cylinder rod chamber with B mouthfuls of the three position four-way directional control valve even
It is logical.
2. according to claim 1 pair of amplitude oil cylinder hydraulic control system, it is characterised in that described the three of the first working position
First segment discharge orifice is offered on oil circuit between A mouthfuls and T mouthfuls of the three position four-way directional control valve of position and four-way reversing valve.
3. according to claim 1 pair of amplitude oil cylinder hydraulic control system, it is characterised in that described pair of amplitude oil cylinder hydraulic pressure
Control system also includes：Regeneration check valve, oil inlet and A mouthfuls of the three position four-way directional control valve and the T of the regeneration check valve
Mouthful between oil communication, and it is described regeneration check valve oil inlet be arranged in A mouthfuls of the three position four-way directional control valve with it is described
Between first segment discharge orifice, the oil circuit between the oil-out of the regeneration check valve and B mouthfuls and P mouthfuls of the three position four-way directional control valve
Connection.
4. according to claim 3 pair of amplitude oil cylinder hydraulic control system, it is characterised in that described the three of the first working position
The second throttle orifice is offered on oil circuit between B mouthfuls and P mouthfuls of the three position four-way directional control valve of position and four-way reversing valve, and it is described
Second throttle orifice is arranged between the oil-out of the regeneration check valve and B mouthfuls of the three position four-way directional control valve.
5. double amplitude oil cylinder hydraulic control systems according to claim any one of 1-4, it is characterised in that described pair of luffing
Oil cylinder hydraulic control system also includes：Pressure limiting valve, the first hydraulic fluid port of the oil inlet of the pressure limiting valve and the sync control device
Connection, the oil-out of the pressure limiting valve is connected with fuel tank, and the pressure value of pressure limiting valve setting is less than or equal to described first
The rated operating pressure value of amplitude oil cylinder or second amplitude oil cylinder.
6. according to claim 5 pair of amplitude oil cylinder hydraulic control system, it is characterised in that described pair of amplitude oil cylinder hydraulic pressure
Control system also includes：Repairing check valve, the oil inlet of the repairing check valve is connected with the oil inlet of the pressure limiting valve, described
The oil-out of repairing check valve is connected with the oil-out of the pressure limiting valve.
7. double amplitude oil cylinder hydraulic control systems according to claim any one of 1-4, it is characterised in that described three four
Logical reversal valve is hydraulic control pilot-operated type three position four-way directional control valve, and the two-bit triplet reversal valve commutates for hydraulic control pilot-operated type two-bit triplet
Valve, described pair of amplitude oil cylinder hydraulic control system also includes：Pilot-actuated valve, the pilot-actuated valve depressurizes including the first threeway
Valve and the second three-way pressure reducing valve, the oil-out of first three-way pressure reducing valve respectively with D mouthfuls of the two-bit triplet reversal valve and
The first pilot control hydraulic fluid port connection of the hydraulic control pilot-operated type three position four-way directional control valve, the oil-out of second three-way pressure reducing valve
Connected with the second pilot control hydraulic fluid port of the hydraulic control pilot-operated type three position four-way directional control valve.
8. double amplitude oil cylinder hydraulic control systems according to claim any one of 1-4, it is characterised in that the synchronous control
Device processed includes syncmotor, and the syncmotor includes：The first coaxially connected two-way quantitative motor and the second two-way quantitative
Motor, the second actuator port of the inserted valve respectively with the first hydraulic fluid port of the first two-way quantitative motor and described second pair
Connected to the first hydraulic fluid port of fixed displacement motor, the nothing of the second hydraulic fluid port of the first two-way quantitative motor and first amplitude oil cylinder
Rod cavity is connected, and the second hydraulic fluid port of the second two-way quantitative motor is connected with the rodless cavity of second amplitude oil cylinder.
9. double amplitude oil cylinder hydraulic control systems according to claim any one of 1-4, it is characterised in that middle position it is described
The 3rd throttle orifice is offered on oil circuit between A mouthfuls and T mouthfuls of the three position four-way directional control valve of three position four-way directional control valve.
10. according to claim 9 pair of amplitude oil cylinder hydraulic control system, it is characterised in that described three four of middle position
The 4th throttle orifice is offered on oil circuit between B mouthfuls and T mouthfuls of the three position four-way directional control valve of logical reversal valve.
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| CN201710057158.6A CN106698199B (en) | 2017-01-23 | 2017-01-23 | A kind of double amplitude oil cylinder hydraulic control systems |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113803310A (en) * | 2021-09-10 | 2021-12-17 | 武汉船用机械有限责任公司 | Double-hydraulic-cylinder synchronous control system and control method thereof |
| CN116202598A (en) * | 2023-01-31 | 2023-06-02 | 常熟市龙腾特种钢有限公司 | Valve table of wire weighing machine |
| CN119489857A (en) * | 2024-11-11 | 2025-02-21 | 中联农业机械股份有限公司 | Hydraulic control system for walking machinery and walking machinery |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3990583A (en) * | 1973-08-23 | 1976-11-09 | Kabushiki Kaisha Komatsu Seisakusho | Device for controlling the boom elevation of a side crane |
| CN102345749A (en) * | 2011-08-29 | 2012-02-08 | 徐州重型机械有限公司 | Flow collecting valve and crane hydraulic control system with the same |
| CN102502433A (en) * | 2011-10-08 | 2012-06-20 | 武汉船用机械有限责任公司 | Variable amplitude hydraulic system of dual-oil-cylinder variable amplitude crane |
| CN202451484U (en) * | 2012-02-28 | 2012-09-26 | 徐州重型机械有限公司 | Double-cylinder synchronization control hydraulic system and crane |
| CN202897848U (en) * | 2012-09-07 | 2013-04-24 | 上海三一科技有限公司 | Mast pulling servo control hydraulic system and crane |
| CN203461740U (en) * | 2013-08-01 | 2014-03-05 | 辽宁瑞丰专用车制造有限公司 | Double-cylinder synchronous luffing system of crane |
| CN203602273U (en) * | 2013-10-09 | 2014-05-21 | 中联重科股份有限公司 | Hydraulic control system for controlling lifting of luffing mast of crane and crane |
| CN104477798A (en) * | 2014-12-10 | 2015-04-01 | 中联重科股份有限公司 | Main arm variable amplitude control system of crane and crane |
| CN105621294A (en) * | 2016-01-29 | 2016-06-01 | 武汉船用机械有限责任公司 | Hydraulically-controlled operation dual-variable-amplitude synchronous adjustment control valve group |
-
2017
- 2017-01-23 CN CN201710057158.6A patent/CN106698199B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3990583A (en) * | 1973-08-23 | 1976-11-09 | Kabushiki Kaisha Komatsu Seisakusho | Device for controlling the boom elevation of a side crane |
| CN102345749A (en) * | 2011-08-29 | 2012-02-08 | 徐州重型机械有限公司 | Flow collecting valve and crane hydraulic control system with the same |
| CN102502433A (en) * | 2011-10-08 | 2012-06-20 | 武汉船用机械有限责任公司 | Variable amplitude hydraulic system of dual-oil-cylinder variable amplitude crane |
| CN202451484U (en) * | 2012-02-28 | 2012-09-26 | 徐州重型机械有限公司 | Double-cylinder synchronization control hydraulic system and crane |
| CN202897848U (en) * | 2012-09-07 | 2013-04-24 | 上海三一科技有限公司 | Mast pulling servo control hydraulic system and crane |
| CN203461740U (en) * | 2013-08-01 | 2014-03-05 | 辽宁瑞丰专用车制造有限公司 | Double-cylinder synchronous luffing system of crane |
| CN203602273U (en) * | 2013-10-09 | 2014-05-21 | 中联重科股份有限公司 | Hydraulic control system for controlling lifting of luffing mast of crane and crane |
| CN104477798A (en) * | 2014-12-10 | 2015-04-01 | 中联重科股份有限公司 | Main arm variable amplitude control system of crane and crane |
| CN105621294A (en) * | 2016-01-29 | 2016-06-01 | 武汉船用机械有限责任公司 | Hydraulically-controlled operation dual-variable-amplitude synchronous adjustment control valve group |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113803310A (en) * | 2021-09-10 | 2021-12-17 | 武汉船用机械有限责任公司 | Double-hydraulic-cylinder synchronous control system and control method thereof |
| CN113803310B (en) * | 2021-09-10 | 2023-07-21 | 武汉船用机械有限责任公司 | Synchronous control system and control method for double hydraulic cylinders |
| CN116202598A (en) * | 2023-01-31 | 2023-06-02 | 常熟市龙腾特种钢有限公司 | Valve table of wire weighing machine |
| CN119489857A (en) * | 2024-11-11 | 2025-02-21 | 中联农业机械股份有限公司 | Hydraulic control system for walking machinery and walking machinery |
| CN119489857B (en) * | 2024-11-11 | 2025-10-10 | 中联农业机械股份有限公司 | Hydraulic control system for walking machinery and walking machinery |
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| CN106698199B (en) | 2018-08-07 |
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