CN104235102B - Getting-on hydraulic system and engineering machinery - Google Patents
Getting-on hydraulic system and engineering machinery Download PDFInfo
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- CN104235102B CN104235102B CN201410448213.0A CN201410448213A CN104235102B CN 104235102 B CN104235102 B CN 104235102B CN 201410448213 A CN201410448213 A CN 201410448213A CN 104235102 B CN104235102 B CN 104235102B
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- 239000003921 oil Substances 0.000 claims description 391
- 239000012530 fluid Substances 0.000 claims description 71
- 239000010720 hydraulic oil Substances 0.000 claims description 34
- 239000007788 liquid Substances 0.000 claims description 16
- 239000002828 fuel tank Substances 0.000 claims description 10
- 230000009471 action Effects 0.000 claims description 7
- 230000000694 effects Effects 0.000 claims description 5
- 230000001737 promoting effect Effects 0.000 claims description 4
- 238000010030 laminating Methods 0.000 claims description 3
- 230000008859 change Effects 0.000 claims description 2
- 230000009467 reduction Effects 0.000 description 6
- 239000002131 composite material Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000033228 biological regulation Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000033001 locomotion Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 150000001875 compounds Chemical class 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 238000005303 weighing Methods 0.000 description 1
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Abstract
The invention discloses a boarding hydraulic system and engineering machinery, wherein the boarding hydraulic system comprises a main oil inlet oil way (4), a main oil return oil way (5) and at least two hydraulic actuating elements, the at least two hydraulic actuating elements are respectively connected with reversing control loops, and each reversing control loop comprises: a first directional valve (1), a first and a second two-way pressure compensation valve (7, 8); the first two-way pressure compensation valve feedback oil ports (71) in the at least two reversing control loops are connected with each other, the second two-way pressure compensation valve feedback oil ports (81) in the at least two reversing control loops are connected with each other, the first two-way pressure compensation valve feedback oil ports (71) and the second two-way pressure compensation valve feedback oil ports (81) in each reversing control loop are connected with each other through respective hydraulic control feedback branch oil paths, and the hydraulic control feedback branch oil paths are connected with each other.
Description
Technical field
The present invention relates to engineering machinery field, in particular it relates to a kind of upper vehicle hydraulic system and engineering machinery.
Background technology
Aerial lift device is different from general engineering machinery, is characterized in that operating frequency is the highest, and load is less, but requirement
The highest safety and reliability.The hydraulic system of aerial lift device is made up of upper vehicle hydraulic system and lower vehicle hydraulic system.
Wherein go up vehicle hydraulic system and generally include changing-breadth system, telescopic system and three fundamental systems of rotary system.Its this get on the bus hydraulic pressure
The hydraulic oil source of system can by executive component respective in hydraulic oil supply to changing-breadth system, telescopic system and rotary system,
And realize the predetermined action got on the bus.
The major defect that upper vehicle hydraulic system of the prior art exists is, when composite move occurs in upper vehicle hydraulic system
Time, in the executive component in changing-breadth system, telescopic system and rotary system hydraulic fluid flow rate distribution inequality, usual hydraulic oil to
The flow that underloading is gone is many, and the flow gone to heavy duty is few, and each executive component linkage is poor.
In consideration of it, be necessary to provide a kind of novel upper vehicle hydraulic system, to overcome or alleviated by drawbacks described above.
Summary of the invention
It is an object of the present invention to provide vehicle hydraulic system in one, on this, vehicle hydraulic system ensure that multiple hydraulic pressure
Linkage during actuator movement, i.e. each hydraulic actuator can obtain identical assignment of traffic so that assignment of traffic
Unrelated with load.
It is a further object to provide a kind of engineering machinery, this engineering machinery uses the liquid of getting on the bus that the present invention provides
Pressure system.
To achieve these goals, the present invention provides vehicle hydraulic system in one, including main oil-feed oil circuit, main oil return circuit
With at least two hydraulic actuator, hydraulic actuator described in this at least two is respectively connected with commutation control loop, wherein,
Each described commutation control loop includes: the first reversal valve, and it includes first to fourth actuator port, and this first reversal valve
Oil-in is connected to described main oil-feed oil circuit, oil return opening is connected to described main oil return circuit, wherein said second actuator port and
The described hydraulic pressure that 3rd actuator port is connected to correspondence via the first working oil path and the second working oil path the most accordingly performs
Element, described first reversal valve at least allows hand over to the first and second duties, wherein in the first duty, described in enter
Hydraulic fluid port and the conducting of the first actuator port, described oil return opening and the 3rd actuator port turn on and described oil-in and oil return opening each other
Cut-off also all ends with described second actuator port and the 4th actuator port；The second duty, described oil-in and the 4th
Actuator port conducting, described oil return opening and the second actuator port turn on and described oil-in and oil return opening ends each other and all with
Described first actuator port and the cut-off of the 3rd actuator port；First and second two-way pressure-compensated valves, described first two-way pressure
The input hydraulic fluid port of recuperation valve is connected to the liquid controling cavity port of described first actuator port and this first two-way pressure-compensated valve and defeated
Oil-out is connected to described first working oil path；The input hydraulic fluid port of described second two-way pressure-compensated valve is connected to described 4th work
Make hydraulic fluid port and the liquid controling cavity port of this second two-way pressure-compensated valve and output oil port is connected to described second working oil path；Institute
State the first and second two-way pressure-compensated valves and respectively further comprise the feedback hydraulic fluid port being connected with respective spring cavity, wherein said first
Enable to when respective described input hydraulic fluid port turns on respective output oil port with the second two-way pressure-compensated valve
Respective described input hydraulic fluid port simultaneously turns on respective feedback hydraulic fluid port；Wherein, in commutation control loop described at least two
Described first two-way pressure-compensated valve feedback hydraulic fluid port is connected to each other, the described 2nd 2 in commutation control loop described at least two
Logical pressure-compensated valve feedback hydraulic fluid port is connected to each other, and the described first two-way pressure-compensated valve in each described commutation control loop is anti-
Feedback hydraulic fluid port and the second two-way pressure-compensated valve feedback hydraulic fluid port are connected to each other by respective hydraulic control feedback branch oil circuit, and each institute
State hydraulic control feedback branch oil circuit to be connected with each other.
Preferably, each described hydraulic control feedback branch oil circuit connects with described main oil return circuit or fuel tank via restricting element
Logical.
Preferably, the described hydraulic control feedback branch oil circuit in each described commutation control loop is all connected to hydraulic control feedback master
Oil circuit, this hydraulic control feedback working connection is connected to described main oil return circuit or fuel tank via described restricting element.
Preferably, on this, vehicle hydraulic system also includes three-way pressure compensating valve, the oiler of described three-way pressure compensating valve
Be connected to described main oil-feed oil circuit, oil-out is connected to described main oil return circuit, and the oiler of described three-way pressure compensating valve is also
Being connected with the liquid controling cavity port of this three-way pressure compensating valve, the spring cavity of this three-way pressure compensating valve is connected to described hydraulic control feedback
Working connection.
Preferably, described hydraulic control feedback working connection is connected to also by the feedback overflow oil circuit being provided with feedback oil circuit overflow valve
Described main oil return circuit or fuel tank.
Preferably, described first reversal valve also have that the middle position of the valve position phase core with this first reversal valve is corresponding the 3rd
Duty, is turned off and described oil return opening at described 3rd duty, described oil-in and first to fourth actuator port
With described second and the 3rd actuator port conducting.
Preferably, the oil-in of described first reversal valve includes that the first oil-in and the second oil-in, oil return opening include
One oil return opening and the second oil return opening, wherein said first oil-in and the second oil-in be connected with described main oil-feed oil circuit respectively,
Described first oil return opening and the second oil return opening are connected with described main oil return circuit respectively.
Preferably, described first reversal valve is electro-hydraulic proportion reversing valve.
Preferably, in commutation control loop at least one described, in described first working oil path and the second working oil path
Being provided with twin-stage fine setting balanced valve group, described twin-stage fine setting balanced valve group includes be arranged in described first working oil path first
Primary sequence valve, first level sequence valve and the second primary sequence valve being arranged in described second working oil path, for the second time
Level sequence valve, wherein said second working oil path is respectively connecting to the hydraulic control end of the described first primary sequence valve and described first time
The hydraulic control end of level sequence valve, the pressure hydraulic control less than described first level sequence valve is opened in the hydraulic control of the described first primary sequence valve
Opening pressure, the oil-in of described first level sequence valve is connected to by the first working oil section of described first working oil path
First hydraulic fluid port of corresponding described hydraulic actuator, the first working oil section of described first working oil path is the most respectively with described
The hydraulic control end of the hydraulic control end of first level sequence valve and the first primary sequence valve connects, the oil-out of described first level sequence valve
Being connected to the oil-in of the described first primary sequence valve, the oil-out of this first primary sequence valve is via described first working oil path
The second working oil section be connected to described second actuator port of described first reversal valve；Described first working oil path connects respectively
It is connected to hydraulic control end and the hydraulic control end of described second subprime sequence valve of the described second primary sequence valve, the described second primary sequence valve
Hydraulic control open pressure less than described second subprime sequence valve hydraulic control open pressure, and the entering of described second subprime sequence valve
Hydraulic fluid port is connected to the second oil of the described hydraulic actuator of correspondence by the first working oil section of described second working oil path
Mouthful, the first working oil section of described second working oil path the most respectively with the hydraulic control end and second of described second subprime sequence valve at the beginning of
The hydraulic control end of level sequence valve connects, and the oil-out of described second subprime sequence valve is connected to the oil-feed of the described second primary sequence valve
Mouthful, the oil-out of this second primary sequence valve is connected to described first via the second working oil section of described second working oil path
Described 3rd actuator port of reversal valve；Described twin-stage fine setting balanced valve group also includes the first check valve and the second check valve, institute
The forward hydraulic fluid port stating the first check valve is connected to the second working oil section of described first working oil path, described first check valve
Reversely hydraulic fluid port is connected to the first working oil section of described first working oil path, and the forward hydraulic fluid port of described second check valve is connected to
Second working oil section of described second working oil path, the reverse hydraulic fluid port of described second check valve is connected to described second working oil
The second working oil section on road.
Preferably, a hydraulic actuator in described at least two hydraulic actuator is boom frame telescopic oil cylinder, institute
State twin-stage fine setting balanced valve group and be arranged on the first working oil path in the commutation control loop that this boom frame telescopic oil cylinder is corresponding and the
In two working oil path.
Preferably, the one in described first working oil path and the second working oil path being provided with one-way balance valve, this is single
The back-moving spring that one-level spool, secondary valve core and the one end with described secondary valve core are connected, described secondary valve is included to balanced valve
Core allows hand over and forms one-way conduction oil circuit and throttling oil for making this secondary valve core match with the valve body of this secondary valve core
Road, the another one in described first working oil path and the second working oil path is connected to institute by the middle oil circuit of one-way balance valve first
State the hydraulic control end of one-level spool, the described middle oil circuit of one-way balance valve first is provided with first throttle valve, this one-way balance valve
The part between the hydraulic control end of described first throttle valve and described one-level spool of the first middle oil circuit is by unidirectional balance
The middle oil circuit of valve second is connected on the hydraulic control end of described secondary valve core, and the middle oil circuit of described one-way balance valve second be provided with
Second throttle, the position of the hydraulic control end being positioned at described one-level spool of described one-way balance valve is provided with elastic spacing moment list
Unit, overcomes so that hydraulic oil can be made to act on this elastic spacing moment unit through the described middle oil circuit of one-way balance valve first
One-step valve core ribbon described in the default resilient force of this elastic spacing moment unit switches with moving described secondary valve core segment stroke
Action, the default elastic force that described elastic spacing moment unit can be overcome of the hydraulic control end of described one-level spool and promote this one
The required minimum oil pressure of level spool is less than the required minimum oil that can promote this secondary valve core of the hydraulic control end of described secondary valve core
Pressure, when hydraulic oil promotes described one-level spool or by described one-way balance valve second by described elastic spacing moment unit
When middle oil circuit promotes described secondary valve core, described valve body and described secondary valve core form throttling oil circuit, so that described execution
Element is connected with the described one in described first working oil path and the second working oil path by described throttling oil circuit, when not having liquid
Force feed promotes described one-level spool or by described one-way balance valve the second middle oil by described elastic spacing moment unit
When road acts on described secondary valve core, described valve body and described secondary valve core reset thus shape under the effect of described back-moving spring
Become one-way conduction oil circuit, so that the described hydraulic actuator of correspondence is by described one-way conduction oil circuit and described first work
Described one in oil circuit and the second working oil path connects, and described one-way conduction oil circuit is configured such that hydraulic oil can be from described
Described one in first working oil path and the second working oil path uniaxially flows to the hydraulic actuator of described correspondence.
Preferably, described elastic spacing moment unit includes the stretching spring being connected to each other and pushes the ball, this stretching spring
Two ends be connected to described one-way balance valve accommodate described one-level spool valve body and described push the ball on, described one-level spool
Valve body be formed with backstop platform overcome the elastic force of described stretching spring to promote described one-level spool so that pushing the ball described in Dang
When driving described secondary valve core to arrive predetermined partial journey, described in push the ball by described backstop platform backstop, and described in push the ball and institute
State backstop platform and seal laminating to be sealed in the valve body of described one-level spool by described one-level spool.
Preferably, described one-way balance valve include respectively with described first working oil path and the hydraulic control end of described secondary valve core
The middle oil circuit of one-way balance valve the 3rd connected, this middle oil circuit of one-way balance valve the 3rd is provided with in one-way balance valve the 3rd
Between oil circuit check valve, the forward port of the described middle oil circuit check valve of one-way balance valve the 3rd is connected to the liquid of described secondary valve core
Control end, reverse port is connected to described first working oil path.
Preferably, the spring cavity of described back-moving spring is connected to executive component and connects oil circuit, and this executive component connects oil circuit
Connect described one-way balance valve and the hydraulic actuator of described correspondence.
Preferably, a hydraulic actuator in hydraulic actuator described in described at least two is luffing range of cantilever support oil
Cylinder, described one-way balance valve is arranged in described first working oil path being connected with the rodless cavity of described boom derricking cylinder.
Preferably, a hydraulic actuator in described at least two hydraulic actuator is rotation of rotary table motor, institute
State main oil-feed oil circuit and main oil return circuit and be connected to described rotation of rotary table horse by pilot valve, the second reversal valve and one-way damper valve
The brake cylinder reached, described pilot valve can be supplied to described braking after being reduced by the pressure of the hydraulic oil of described main oil-feed oil circuit
Oil cylinder.
Preferably, described first working oil path and the second working oil path are connected to oil by overflow working oil path the most respectively
Case.
Preferably, described main oil-feed oil circuit is connected to main oil feed pump and emergency pump.
Additionally, the present invention also provides for a kind of engineering machinery, wherein, this engineering machinery includes according to institute in technique scheme
The upper vehicle hydraulic system stated.
By technique scheme, due to commutation control described at least two in the upper vehicle hydraulic system that the present invention provides
Described first two-way pressure-compensated valve feedback hydraulic fluid port in loop is connected to each other, the institute in commutation control loop described at least two
State the second two-way pressure-compensated valve feedback hydraulic fluid port to be connected to each other, the described first two-way pressure in each described commutation control loop
Recuperation valve feedback hydraulic fluid port and the second two-way pressure-compensated valve feedback hydraulic fluid port are connected to each other by respective hydraulic control feedback branch oil circuit,
And each described hydraulic control feedback branch oil circuit is connected with each other, so in the case of underfed, be associated each two-way
By self regulation, pressure-compensated valve guarantees that its spring cavity reaches dynamic equilibrium and equal with the pressure of liquid controling cavity, so that
The downstream pressure of each the first reversal valve is equal, and owing to the oil-in of each the first reversal valve is all connected to main oil-feed oil circuit,
So the upstream pressure of each the first reversal valve is equal, so, before and after each first reversal valve, pressure reduction is equal, so by each
The flow of the hydraulic oil that individual first reversal valve enters corresponding hydraulic actuator is equal so that assignment of traffic is unrelated with load,
Ensure that linkage when multiple hydraulic actuator moves.
Other features and advantages of the present invention will be described in detail in detailed description of the invention part subsequently.
Accompanying drawing explanation
Accompanying drawing is used to provide a further understanding of the present invention, and constitutes the part of description, with following tool
Body embodiment is used for explaining the present invention together, but is not intended that limitation of the present invention.In the accompanying drawings:
Fig. 1 is the hydraulic principle schematic diagram of upper vehicle hydraulic system according to the embodiment of the present invention.
Fig. 2 is the first reversal valve in Fig. 1, the first two-way pressure-compensated valve and the second two-way pressure compensation valve position
Partial enlarged drawing.
Fig. 3 is showing the enlarged diagram of twin-stage fine setting balanced valve group according to the embodiment of the present invention.
Fig. 4 is showing the enlarged diagram of one-way balance valve according to the embodiment of the present invention.
Description of reference numerals
1 first reversal valve 2 first working oil path
3 second working oil path 4 main oil-feed oil circuit
5 main oil return circuit 6 three-way pressure compensating valves
7 first two-way pressure-compensated valve 8 second two-way pressure-compensated valves
9 twin-stage fine setting balanced valve group 10 boom frame telescopic oil cylinders
11 one-way balance valve 12 boom derricking cylinder
13 rotation of rotary table motor 14 pilot valves
15 second reversal valve 16 one-way damper valves
The 17 main oil feed pumps of overflow working oil path 18
19 emergency pump 20 hydraulic control feedback working connections
21 Flow-rate adjustment input oil circuit 22 Flow-rate adjustment output circuits
23 feedback oil circuit overflow valve 71 first two-way pressure-compensated valve feedback hydraulic fluid ports
The 81 second two-way pressure-compensated valve primary sequence valves of feedback hydraulic fluid port 91 first
92 first primary sequence valves of level sequence valve 93 second
The 94 middle oil circuits of second subprime sequence valve 95 first
First working oil section of 96 second middle oil circuit 97 first working oil path
98 the 3rd middle oil circuits of middle oil circuit 99 the 4th
First working oil section of 100 second working oil path
101 first oil-in 102 second oil-ins
103 first oil return opening 104 second oil return openings
105 first actuator port 106 second actuator ports
107 the 3rd actuator port 108 the 4th actuator ports
111 one-level spool 112 secondary valve cores
113 one-way balance valve first middle oil circuit 114 one-way balance valve the second middle oil circuits
115 one-way balance valve the 3rd middle oil circuit 116 middle oil circuit check valve of one-way balance valve the 3rd
Detailed description of the invention
Below in conjunction with accompanying drawing, the detailed description of the invention of the present invention is described in detail.It should be appreciated that this place is retouched
The detailed description of the invention stated is merely to illustrate and explains the present invention, is not limited to the present invention.
See Fig. 1 and Fig. 2, according to an aspect of the present invention, it is provided that vehicle hydraulic system in one, including main oil-feed oil circuit
4, main oil return circuit 5 and at least two hydraulic actuator, this at least two hydraulic actuator is respectively connected with commutation control
Loop, wherein, each commutation control loop includes: the first reversal valve 1, this first reversal valve include the first actuator port 105,
Two actuator port the 106, the 3rd actuator port 107 and the 4th actuator ports 108, and the oil-in of this first reversal valve 1 is connected to
Main oil-feed oil circuit 4, oil return opening are connected to main oil return circuit 5, and wherein the second actuator port 106 and the 3rd actuator port 107 are respective
Accordingly via the first working oil path 2 and the second working oil path 3 be connected to correspondence hydraulic actuator, the first reversal valve 1 to
Allowing hand over less to the first and second duties, wherein in the first duty, oil-in and the first actuator port 105 are led
Logical, oil return opening and the 3rd actuator port 107 turns on and oil-in and oil return opening ends each other and all with the second actuator port 106
End with the 4th actuator port 108；Turn at the second duty, oil-in and the 4th actuator port 108, oil return opening and second
Actuator port 106 turn on and oil-in and oil return opening ends each other and all with the first actuator port 105 and the 3rd actuator port
107 cut-offs；Certainly, the first reversal valve 1 can also have threeth corresponding with the bit positions of the spool of this first reversal valve 1
Duty, in the 3rd duty, the oil-in of the first reversal valve 1 can be with first actuator port the 105, second actuator port
106, the 3rd actuator port 107 and the 4th actuator port 108 is turned off and the oil return opening of the first reversal valve 1 can be with the second work
Making hydraulic fluid port 106 and the 3rd actuator port 106 turns on, specifically, the oil-in of the first reversal valve 1 can include the first oil-in
101 and second oil-in 102, oil return opening can include the first oil return opening 103 and the second oil return opening 104, wherein the first oil-in
101 and second oil-in 102 can be connected with main oil-feed oil circuit 4 respectively, the first oil return opening 103 and the second oil return opening 104 are permissible
It is connected with main oil return circuit 5 respectively, but the invention is not restricted to this.Each commutation control loop also includes the first two-way pressure compensation
Valve 7 and the second two-way pressure-compensated valve 8, the input hydraulic fluid port of the first two-way pressure-compensated valve 7 is connected to the first actuator port 105 He
The liquid controling cavity port of this first two-way pressure-compensated valve 7 and the output oil port of the first two-way pressure-compensated valve 7 are connected to the first work
Make oil circuit 2；The input hydraulic fluid port of the second two-way pressure-compensated valve 8 is connected to the 4th actuator port 108 and this second two-way pressure is mended
The output oil port of the liquid controling cavity port and the second two-way pressure-compensated valve 8 of repaying valve 8 is connected to the second working oil path 3；First two-way
Pressure-compensated valve 7 and the second two-way pressure-compensated valve 8 respectively further comprise the two-way pressure compensation being connected with respective spring cavity
Valve feedback hydraulic fluid port 71 and the second two-way pressure-compensated valve feedback hydraulic fluid port 81, wherein the first two-way pressure-compensated valve 7 is in the first two-way
The one or two can be made under the state of the input hydraulic fluid port of pressure-compensated valve 7 and the output oil port conducting of the first two-way pressure-compensated valve 7
Input hydraulic fluid port and the first two-way pressure-compensated valve feedback hydraulic fluid port 71 of logical pressure-compensated valve 7 simultaneously turn on, and the second two-way pressure is mended
Repay the state that valve 8 turns at the input hydraulic fluid port of the second two-way pressure-compensated valve 8 and the output oil port of the second two-way pressure-compensated valve 8
Under enable to the input hydraulic fluid port of the second two-way pressure-compensated valve 8 and the second two-way pressure-compensated valve feedback hydraulic fluid port 81 is led simultaneously
Logical；Wherein, the first two-way pressure-compensated valve feedback hydraulic fluid port 71 at least two commutation control loop is connected to each other, at least two
The second two-way pressure-compensated valve feedback hydraulic fluid port 81 in commutation control loop is connected to each other, first in each commutation control loop
Two-way pressure-compensated valve feedback hydraulic fluid port 71 and the second two-way pressure-compensated valve feedback hydraulic fluid port 81 are by respective hydraulic control feedback branch
Oil circuit is connected to each other, and each hydraulic control feedback branch oil circuit is connected with each other.Wherein, the first reversal valve 1 preferably electric-hydraulic proportion is changed
To valve, but the invention is not restricted to this.
First be as noted previously, as at least two commutation control loop in the upper vehicle hydraulic system that the present invention provides
Two-way pressure-compensated valve feedback hydraulic fluid port 71 is connected to each other, and the second two-way pressure-compensated valve at least two commutation control loop is anti-
Feedback hydraulic fluid port 81 is connected to each other, the first two-way pressure-compensated valve feedback hydraulic fluid port 71 and the second two-way pressure in each commutation control loop
Force compensating valve feedback hydraulic fluid port 81 is connected to each other by respective hydraulic control feedback branch oil circuit, and each hydraulic control feedback branch oil circuit phase
Connect, so in the case of underfed, be associated each two-way pressure-compensated valve guaranteed by self regulation
Its spring cavity reaches dynamic equilibrium and equal with the pressure of liquid controling cavity, so that the downstream pressure phase of each the first reversal valve 1
Deng, and owing to the oil-in of each the first reversal valve 1 is all connected to main oil-feed oil circuit 4, so before the valve of each the first reversal valve 1
Pressure is equal, and so, before and after each first reversal valve 1, pressure reduction is equal, so entering correspondence by each first reversal valve 1
The flow of the hydraulic oil of hydraulic actuator is equal so that assignment of traffic is unrelated with load, it is ensured that multiple hydraulic actuators
Linkage during motion.
Specifically, each hydraulic control feedback branch oil circuit can connect with main oil return circuit 5 or fuel tank via restricting element.Respectively
Hydraulic control feedback branch oil circuit in individual commutation control loop can be all connected to hydraulic control feedback working connection 20, and main oil is fed back in this hydraulic control
Road 20 is connected to main oil return circuit 5 or fuel tank via restricting element.
Additionally, vehicle hydraulic system can also include three-way pressure compensating valve 6, the oiler of three-way pressure compensating valve 6 on this
Oil circuit 21 is connected to main oil-feed oil circuit 4, the oil-out of three-way pressure compensating valve 6 can be via stream can to pass through Flow-rate adjustment input
Amount regulation output circuit 22 is connected to main oil return circuit 5, and the oiler of three-way pressure compensating valve 6 can also be mended with this three-way pressure
The liquid controling cavity port repaying valve 6 connects, and the spring cavity of this three-way pressure compensating valve 6 can be connected to hydraulic control feedback working connection 20, this
By the load feedback effect of three-way pressure compensating valve 6, the setting of sample, can ensure that the pressure reduction after and before the valve of the first reversal valve 1 is permanent
Fixed, thus the flow by the hydraulic oil of the first reversal valve 1 is constant, so that the hydraulic pressure being connected to this first reversal valve 1 performs
The execution speed of element is unrelated with load.It should be added that, this three-way pressure compensating valve 6 is particularly suited at liquid of getting on the bus
Single executive component in pressure system carries out ensureing during action that the pressure reduction after and before the valve of the first reversal valve 1 is constant, because on Tong Chang
When composite move (action simultaneously of the most multiple hydraulic actuators) occurs in vehicle hydraulic system, the flow that upper vehicle hydraulic system provides can
Can cannot meet metered flow needed for composite move, now three-way pressure compensating valve 6 can be closed because of underfed, therefore upper
When composite move occurs in vehicle hydraulic system, ensure each the first reversal valve generally by each two-way pressure-compensated valve above-mentioned
Before and after 1, pressure reduction is equal, due to specifically illustrated above each two-way pressure-compensated valve be how to ensure each first
Before and after reversal valve 1, pressure reduction is equal, repeats no more here.
According to the preferred embodiment of the present invention, hydraulic control feedback working connection 20 can also be by being provided with feedback oil circuit overflow valve
The feedback overflow oil circuit of 23 is connected to main oil return circuit 5 or fuel tank.
From Fig. 1 and Fig. 3 it can be seen that at least one commutation control loop, the first working oil path 2 and the second work
Being also provided with twin-stage fine setting balanced valve group 9 on oil circuit 3, twin-stage fine setting balanced valve group 9 can include being arranged on the first work
Primary 91, first the level sequence valve 92 of sequence valve of on oil circuit 2 first and the second primary being arranged in the second working oil path 3
Sequence valve 93, second subprime sequence valve 94, wherein the second working oil path 3 can be connected at the beginning of first by the first middle oil circuit 95
The hydraulic control end of level sequence valve 91, and the first middle oil circuit 95 can be connected to first level sequence valve by the second middle oil circuit 96
The hydraulic control end of 92, the hydraulic control unlatching pressure of the first primary sequence valve 91 is less than the hydraulic control of first level sequence valve 92 and opens pressure,
The oil-in of first level sequence valve 92 can be connected to the liquid of correspondence by the first working oil section 97 of the first working oil path
Pressure executive component the first hydraulic fluid port, the first working oil section 97 of the first working oil path can also respectively with first level sequence valve
The hydraulic control end of the hydraulic control end of 92 and the first primary sequence valve 91 connects, and the oil-out of first level sequence valve 92 can be connected to the
The oil-in of one primary sequence valve 91, the oil-out of this first primary sequence valve 91 can be via the second of the first working oil path 2
Working oil section is connected to the second actuator port 106 of the first reversal valve；First working oil path 2 can pass through the 3rd middle oil circuit
The 98 hydraulic control ends being connected to the second primary sequence valve 93, and the 3rd middle oil circuit 98 can be connected to by the 4th middle oil circuit 99
The hydraulic control end of second subprime sequence valve 94, the hydraulic control of the second primary sequence valve 93 opens pressure less than second subprime sequence valve 94
Hydraulic control open pressure, and the oil-in of second subprime sequence valve 94 can be by the first working oil section of the second working oil path
Second hydraulic fluid port of 100 hydraulic actuators being connected to correspondence, the first working oil section 100 of the second working oil path can also be divided
The hydraulic control end of not primary with the hydraulic control end of second subprime sequence valve 94 and second sequence valve 93 is connected, second subprime sequence valve 94
Oil-out can be connected to the oil-in of the second primary sequence valve 93, and the oil-out of this second primary sequence valve 93 can be via the
Second working oil section of two working oil path is connected to the 3rd actuator port 107 of the first reversal valve；Twin-stage fine setting balanced valve group 9
Can also include the first check valve and the second check valve, the forward hydraulic fluid port of the first check valve can be connected to the first working oil path 2
The second working oil section, the reverse hydraulic fluid port of the first check valve can be connected to the first working oil section of the first working oil path
97, the forward hydraulic fluid port of the second check valve can be connected to the second working oil section of the second working oil path 3, the second check valve anti-
The second working oil section 100 of the second working oil path can be connected to hydraulic fluid port.
A hydraulic actuator in above at least two hydraulic actuator can be boom frame telescopic oil cylinder 10, twin-stage
The first working oil path 2 and second that fine setting balanced valve group 9 is arranged in the commutation control loop of this boom frame telescopic oil cylinder 10 correspondence
In working oil path 3, and the invention is not restricted to this.When being provided with in the commutation control loop of boom frame telescopic oil cylinder 10, twin-stage fine setting is flat
During weighing apparatus valve group 9, as a example by operating mode retracted by boom frame telescopic oil cylinder 10, illustrate how twin-stage fine setting balanced valve group 9 works, specifically
For, referring also to Fig. 1 and Fig. 3, when boom frame telescopic oil cylinder 10 is retracted, hydraulic oil enters twin-stage fine setting from the second working oil path 3
Two-way hydraulic oil, road hydraulic oil approach second check valve it is divided into enter the rod chamber of jib telescopic oil cylinder 10 after balanced valve group 9,
Another road hydraulic oil enters the first middle oil circuit 95, and the hydraulic oil subsequently into the first middle oil circuit 95 is further divided into two-way hydraulic oil
It is respectively acting on hydraulic control end and the hydraulic control end of first level sequence valve 92 of a primary sequence valve 91, due to the first primary sequence valve
The hydraulic control of 91 is opened pressure and is opened pressure less than the hydraulic control of first level sequence valve 92, so that the valve of a primary sequence valve 91
The spool of core and first level sequence valve 92 is opened sequentially, serves the effect of a power of contending with in the process, increases
Add the back pressure of load so that the unlatching of twin-stage fine setting balanced valve group 9 is more steady.
Can be provided with in one from Fig. 1 and Fig. 4 it can be seen that in the first working oil path 2 and the second working oil path 3
One-way balance valve 11, this one-way balance valve 11 can include one-level spool 111, secondary valve core 112 and with the one of secondary valve core 112
The back-moving spring that end connects, secondary valve core 112 allows hand over the valve body for making this secondary valve core 112 and this secondary valve core 112
Matching and form one-way conduction oil circuit and throttling oil circuit, the another one in the first working oil path 2 and the second working oil path 3 is permissible
The hydraulic control end of one-level spool 111, the middle oil circuit of one-way balance valve first it is connected to by the middle oil circuit of one-way balance valve first 113
First throttle valve can be provided with on 113, this middle oil circuit of one-way balance valve first 113 be positioned at first throttle valve and one-step valve
Part between the hydraulic control end of core 111 is connected to the hydraulic control of secondary valve core 112 by the middle oil circuit of one-way balance valve second 114
End, and can be provided with second throttle on the middle oil circuit of one-way balance valve second 114, one-way balance valve 11 be positioned at one-step valve
The position of the hydraulic control end of core 111 can be provided with elastic spacing moment unit, so that hydraulic oil can be made through one-way balance valve
One middle oil circuit 113 acts on this elastic spacing moment unit and overcomes the default resilient force of this elastic spacing moment unit
One-level spool 111 drive secondary valve core 112 partial journey ground switching action, the hydraulic control end of one-level spool 111 can overcome bullet
Property the default elastic force of spacing torque unit and promote the required minimum oil pressure of this one-level spool 111 less than secondary valve core 112
The required minimum oil pressure that can promote this secondary valve core of hydraulic control end, when hydraulic oil promotes one-level by elastic spacing moment unit
Spool 111 or when promoting secondary valve core 112 by the middle oil circuit of one-way balance valve second 114, valve body and secondary valve core 112 shape
Become throttling oil circuit, so that executive component is by the one in throttling oil circuit and the first working oil path 2 and the second working oil path 3 even
Connect, promote one-level spool 111 when not having hydraulic oil to pass through elastic spacing moment unit or pass through in the middle of one-way balance valve second
When oil circuit 114 acts on secondary valve core 112, valve body and secondary valve core 112 reset under the effect of back-moving spring thus form list
To conducting oil circuit, so that the hydraulic actuator of correspondence is by one-way conduction oil circuit and the first working oil path 2 and the second work
One in oil circuit 3 connects, and one-way conduction oil circuit is configured such that hydraulic oil can be from the first working oil path 2 and the second working oil
One in road 3 uniaxially flows to the hydraulic actuator of correspondence.
Specifically, elastic spacing moment unit can include the stretching spring being connected to each other and push the ball, this stretching spring
On two ends can be connected to the valve body of the receiving one-level spool 111 of one-way balance valve 11 and push the ball, the valve of one-level spool 111
Body is formed with backstop platform, so that overcoming the elastic force of stretching spring when pushing the ball and promoting one-level spool 111 to drive secondary valve core
112 when arriving predetermined partial journey, pushes the ball by backstop platform backstop, and pushes the ball and backstop platform seals laminating with by one-level spool
In 111 valve bodies being sealed in one-level spool 111.Additionally, one-way balance valve 11 can also include respectively with the first working oil path 2 and
The middle oil circuit 115 of one-way balance valve the 3rd that the hydraulic control end of secondary valve core 112 connects, this middle oil circuit of one-way balance valve the 3rd
The middle oil circuit check valve 116 of one-way balance valve the 3rd, the middle oil circuit check valve of one-way balance valve the 3rd can be provided with on 115
The forward port of 116 is connected to the hydraulic control end of secondary valve core 112, and reverse port is connected to the first working oil path 2, back-moving spring
Spring cavity can be connected to executive component and connect oil circuit, and this executive component connects oil circuit can connect one-way balance valve 11 and correspondence
Hydraulic actuator, so can by the pressure oil in the spring cavity of back-moving spring by connect one-way balance valve 11 arrange in time
Remove.
A hydraulic actuator in above at least two hydraulic actuator can be boom derricking cylinder 12, unidirectional
Balanced valve 11 can be arranged in the first working oil path that the rodless cavity with boom derricking cylinder 12 is connected.Work as boom derricking cylinder
When the commutation control loop of 12 is provided with one-way balance valve 11, decline explanation as a example by operating mode by the luffing of boom derricking cylinder 12
How one-way balance valve 11 works, and specifically, referring also to Fig. 1 and Fig. 4, exemplary in figure shows one-way balance valve
11 are arranged in the first working oil path 2, and the second working oil path 3 is connected to one by the middle oil circuit of one-way balance valve first 113
The hydraulic control end of level spool 111, a part of hydraulic oil arm entry when boom derricking cylinder 12 declines, in the second working oil path 3
In the rod chamber of frame amplitude oil cylinder 12, another part hydraulic oil arrives one-level after entering the middle oil circuit of one-way balance valve first 113
The hydraulic control end of spool 111, then promotes one-level spool 111 to drive secondary valve core 112 to move to by elastic spacing moment unit
(this partial journey is the LAP in the complete stroke that secondary valve core 112 can move to partial journey, such as, works as secondary valve
When core 112 can move to right position from left position, the position that the described partial journey of secondary valve core 112 is corresponding is this left position and right position
Between a certain position), at this moment, one-level spool 111 is limited (at this by the position-limiting action of elastic spacing moment unit
In the preferred implementation of bright offer, owing to pushing the ball by backstop platform backstop, pushed away further so one-level spool 111 can not push the ball
Dynamic and limited), then hydraulic oil arrives the hydraulic control end of secondary valve core 112 through the middle oil circuit of one-way balance valve second 114,
Thus promoting secondary valve core 112 to move further so that the spool of one-way balance valve 11 fully opens (at this moment one-way balance valve 11
Still be formed as the oil circuit that throttles) so that boom derricking cylinder 12 uniform descent under the constraint of throttling oil circuit, at said process
In, owing to needing when the hydraulic oil in the middle oil circuit of balanced valve second 114 reaches the minimum pressure that can promote secondary valve core 112
Want certain and build the pressure time, so that one-way balance valve 11 can more slowly be opened, it is to avoid traditional balanced valve is in pressure
Power reaches unexpected standard-sized sheet during pilot pressure and the phenomenon of build-up of pressure impact.Additionally, when acting on luffing range of cantilever support oil without hydraulic oil
During cylinder 12, one-way balance valve 11 returns to be formed the position of one-way conduction oil circuit under the reset response of back-moving spring, with preventing arm
Hydraulic oil in the rodless cavity of frame amplitude oil cylinder 12 leaks.
Return from figure 1 it appears that a hydraulic actuator at least two hydraulic actuator can be turntable
Turn motor 13, main oil-feed oil circuit 4 and main oil return circuit 5 to be connected by pilot valve the 14, second reversal valve 15 and one-way damper valve 16
To the brake cylinder of rotation of rotary table motor 13, pilot valve 14 can be supplied after being reduced by the pressure of the hydraulic oil of main oil-feed oil circuit 4
To brake cylinder, when the second reversal valve 15 control rotation of rotary table motor 13 start time, hydraulic oil can pass through one-way damper valve 16
In check valve enter brake cylinder, when the second reversal valve 15 control rotation of rotary table motor 13 braking stop time, in brake cylinder
Hydraulic oil slowly can be laid down, such that it is able to rotation of rotary table motor 13 is realized soon by the orifice plug in one-way damper valve 16
Change down pass, reach steady shock-free purpose.
Additionally, the first working oil path 2 and the second working oil path 3 can also be connected to oil by overflow working oil path 17 respectively
Case.Main oil-feed oil circuit 4 can be connected to main oil feed pump 18 and emergency pump 19, so that vehicle hydraulic system has one on this
Fixed emergent compensation function.
According to another aspect of the present invention, it is provided that a kind of engineering machinery, wherein, this engineering machinery includes according to above-mentioned
Upper vehicle hydraulic system described in technical scheme, just owing to being enumerated above the plurality of advantages of vehicle hydraulic system on this, this is undoubtedly
Improve overall performance and the quality including the engineering machinery of vehicle hydraulic system on this.
The preferred embodiment of the present invention is described in detail above in association with accompanying drawing, but, the present invention is not limited to above-mentioned reality
Execute the detail in mode, in the technology concept of the present invention, technical scheme can be carried out multiple letter
Monotropic type, these simple variant belong to protection scope of the present invention.
It is further to note that each the concrete technical characteristic described in above-mentioned detailed description of the invention, at not lance
In the case of shield, can be combined by any suitable means.In order to avoid unnecessary repetition, the present invention to various can
The compound mode of energy illustrates the most separately.
Additionally, combination in any can also be carried out between the various different embodiment of the present invention, as long as it is without prejudice to this
The thought of invention, it should be considered as content disclosed in this invention equally.
Claims (19)
1. a upper vehicle hydraulic system, including main oil-feed oil circuit (4), main oil return circuit (5) and at least two hydraulic actuator,
Hydraulic actuator described in this at least two is respectively connected with commutation control loop, and wherein, each described commutation control loop is wrapped
Include:
First reversal valve (1), it includes first to fourth actuator port (105,106,107,108), and this first reversal valve (1)
Oil-in be connected to described main oil-feed oil circuit (4), oil return opening is connected to described main oil return circuit (5), wherein said second work
Make hydraulic fluid port (106) and the 3rd actuator port (107) each accordingly via the first working oil path (2) and the second working oil path (3)
Being connected to the described hydraulic actuator of correspondence, described first reversal valve (1) at least allows hand over to the first and second work shapes
State, wherein in the first duty, described oil-in and the first actuator port (105) conducting, described oil return opening and the 3rd work
Hydraulic fluid port (107) conducting and described oil-in and oil return opening ends each other and all with described second actuator port (106) and the 4th work
Make hydraulic fluid port (108) cut-off；In the second duty, described oil-in and the conducting of the 4th actuator port (108), described oil return opening with
Second actuator port (106) conducting and described oil-in and oil return opening ends each other and all with described first actuator port (105)
With the 3rd actuator port (107) cut-off；
First and second two-way pressure-compensated valves (7,8), the input hydraulic fluid port of described first two-way pressure-compensated valve (7) is connected to institute
State the first actuator port (105) and the liquid controling cavity port of this first two-way pressure-compensated valve (7) and output oil port is connected to described
First working oil path (2)；The input hydraulic fluid port of described second two-way pressure-compensated valve (8) is connected to described 4th actuator port
And the liquid controling cavity port of this second two-way pressure-compensated valve (8) and output oil port are connected to described second working oil path (108)
(3)；Described first and second two-way pressure-compensated valves (7,8) respectively further comprise the feedback hydraulic fluid port being connected with respective spring cavity
(71,81), wherein said first and second two-way pressure-compensated valves (7,8) are in respective described input hydraulic fluid port and respective output
Enable to respective described input hydraulic fluid port under the state of hydraulic fluid port conducting simultaneously turn on respective feedback hydraulic fluid port (71,81)；
Wherein, described first two-way pressure-compensated valve feedback hydraulic fluid port (71) in commutation control loop described at least two connects each other
Connecing, described second two-way pressure-compensated valve feedback hydraulic fluid port (81) in commutation control loop described at least two is connected to each other, respectively
Described first two-way pressure-compensated valve feedback hydraulic fluid port (71) and the second two-way pressure-compensated valve in individual described commutation control loop
Feedback hydraulic fluid port (81) is connected to each other by respective hydraulic control feedback branch oil circuit, and each described hydraulic control feedback branch oil circuit is mutual
Connect.
Upper vehicle hydraulic system the most according to claim 1, it is characterised in that each described hydraulic control feedback branch oil circuit via
Restricting element connects with described main oil return circuit (5) or fuel tank.
Upper vehicle hydraulic system the most according to claim 1, it is characterised in that described in each described commutation control loop
Hydraulic control feedback branch oil circuit is all connected to hydraulic control feedback working connection (20), and this hydraulic control feedback working connection (20) is via restricting element even
It is connected to described main oil return circuit (5) or fuel tank.
Upper vehicle hydraulic system the most according to claim 3, it is characterised in that on this, vehicle hydraulic system also includes three-way pressure
Recuperation valve (6), the oiler of described three-way pressure compensating valve (6) is connected to described main oil-feed oil circuit (4), oil-out is connected to institute
State main oil return circuit (5), the oiler of described three-way pressure compensating valve (6) also with the liquid controling cavity of this three-way pressure compensating valve (6)
Port connects, and the spring cavity of this three-way pressure compensating valve (6) is connected to described hydraulic control feedback working connection (20).
Upper vehicle hydraulic system the most according to claim 4, it is characterised in that described hydraulic control feedback working connection (20) also by
The feedback overflow oil circuit being provided with feedback oil circuit overflow valve (23) is connected to described main oil return circuit (5) or fuel tank.
Upper vehicle hydraulic system the most according to claim 1, it is characterised in that described first reversal valve (1) also has and is somebody's turn to do
The 3rd duty that the middle position of the valve position phase core of the first reversal valve (1) is corresponding, in described 3rd duty, described oil-feed
Mouthful it is turned off with first to fourth actuator port (105,106,107,108) and described oil return opening and described second and the 3rd work
Make hydraulic fluid port (106,107) conducting.
Upper vehicle hydraulic system the most according to claim 6, it is characterised in that the oil-in bag of described first reversal valve (1)
Include the first oil-in (101) and the second oil-in (102), oil return opening include the first oil return opening (103) and the second oil return opening
(104), wherein said first oil-in (101) and the second oil-in (102) are connected with described main oil-feed oil circuit (4) respectively, institute
State the first oil return opening (103) and the second oil return opening (104) is connected with described main oil return circuit (5) respectively.
Upper vehicle hydraulic system the most according to any one of claim 1 to 7, it is characterised in that described first reversal valve (1)
For electro-hydraulic proportion reversing valve.
Upper vehicle hydraulic system the most according to any one of claim 1 to 7, it is characterised in that change described at least one
To controlling in loop, described first working oil path (2) and the second working oil path (3) are provided with twin-stage fine setting balanced valve group (9),
The first primary sequence valve (91) that described twin-stage fine setting balanced valve group (9) includes being arranged on described first working oil path (2), the
Level sequence valve (92) and the second primary sequence valve (93) being arranged on described second working oil path (3), second subprime
Sequence valve (94), wherein
Described second working oil path (3) is respectively connecting to the hydraulic control end of the described first primary sequence valve (91) and described first level
The hydraulic control end of sequence valve (92), the hydraulic control of the described first primary sequence valve (91) opens pressure less than described first level sequence valve
(92) pressure, the oil-in of described first level sequence valve (92) the first work by described first working oil path are opened in hydraulic control
Make the first hydraulic fluid port that oil circuit section (97) is connected to the described hydraulic actuator of correspondence, the first work of described first working oil path
The hydraulic control end of oil circuit section (97) sequence valve (91) primary with the hydraulic control end of described first level sequence valve (92) and first the most respectively
Connecting, the oil-out of described first level sequence valve (92) is connected to the oil-in of described first primary sequence valve (91), and this is the years old
The oil-out of one primary sequence valve (91) is connected to described first via the second working oil section of described first working oil path (2)
Described second actuator port (106) of reversal valve；
Described first working oil path (2) is respectively connecting to the hydraulic control end of the described second primary sequence valve (93) and described second subprime
The hydraulic control end of sequence valve (94), the hydraulic control of the described second primary sequence valve (93) opens pressure less than described second subprime sequence valve
(94) hydraulic control open pressure, and the oil-in of described second subprime sequence valve (94) by described second working oil path the
One working oil section (100) is connected to second hydraulic fluid port of described hydraulic actuator of correspondence, the of described second working oil path
One working oil section (100) sequence valve (93) primary with the hydraulic control end of described second subprime sequence valve (94) and second the most respectively
Hydraulic control end connects, and the oil-out of described second subprime sequence valve (94) is connected to the oil-feed of the described second primary sequence valve (93)
Mouthful, the oil-out of this second primary sequence valve (93) is connected to described via the second working oil section of described second working oil path
Described 3rd actuator port (107) of the first reversal valve；
Described twin-stage fine setting balanced valve group (9) also includes the first check valve and the second check valve, the forward of described first check valve
Hydraulic fluid port is connected to the second working oil section of described first working oil path (2), and the reverse hydraulic fluid port of described first check valve is connected to
First working oil section (97) of described first working oil path, the forward hydraulic fluid port of described second check valve is connected to described second work
Making the second working oil section of oil circuit (3), the reverse hydraulic fluid port of described second check valve is connected to the of described second working oil path
Two working oil sections (100).
Upper vehicle hydraulic system the most according to claim 9, it is characterised in that in described at least two hydraulic actuator
A hydraulic actuator be boom frame telescopic oil cylinder (10), described twin-stage fine setting balanced valve group (9) be arranged on this boom frame telescopic
In the first working oil path (2) in the commutation control loop that oil cylinder (10) is corresponding and the second working oil path (3).
11. upper vehicle hydraulic systems according to any one of claim 1 to 7, it is characterised in that described first working oil path
(2) being provided with one-way balance valve (11) in the one in and the second working oil path (3), this one-way balance valve (11) includes one-step valve
The back-moving spring that core (111), secondary valve core (112) and the one end with described secondary valve core (112) are connected, described secondary valve core
(112) allow hand over and form one-way conduction for making this secondary valve core (112) match with the valve body of this secondary valve core (112)
Oil circuit and throttling oil circuit, the another one in described first working oil path (2) and the second working oil path (3) passes through one-way balance valve the
One middle oil circuit (113) is connected to the hydraulic control end of described one-level spool (111), the described middle oil circuit of one-way balance valve first
(113) be provided with first throttle valve on, the middle oil circuit of this one-way balance valve first (113) be positioned at described first throttle valve and institute
The part stated between the hydraulic control end of one-level spool (111) is connected to described two by the middle oil circuit of one-way balance valve second (114)
The hydraulic control end of level spool (112), and it is provided with second throttle on the middle oil circuit of described one-way balance valve second (114), described
The position of the hydraulic control end being positioned at described one-level spool (111) of one-way balance valve (11) is provided with elastic spacing moment unit, with
Hydraulic oil can be made to act on this elastic spacing moment unit through the middle oil circuit of described one-way balance valve first (113) and overcome
One-level spool (111) described in the default resilient force of this elastic spacing moment unit drives described secondary valve core (112) part
Stroke ground switching action, the hydraulic control end of described one-level spool (111) can overcome described elastic spacing moment unit preset
Elastic force and promote the required minimum oil pressure of this one-level spool (111) the hydraulic control end less than described secondary valve core (112) can
Promote the required minimum oil pressure of this secondary valve core, when hydraulic oil promotes described one-level spool by described elastic spacing moment unit
(111) when or promoting described secondary valve core (112) by the middle oil circuit of described one-way balance valve second (114), described valve body
Throttling oil circuit is formed, so that described executive component is by described throttling oil circuit and described first with described secondary valve core (112)
Described one in working oil path (2) and the second working oil path (3) connects, when not having hydraulic oil by described elastic spacing moment
Unit promotes described one-level spool (111) or acts on described two by the middle oil circuit of described one-way balance valve second (114)
During level spool (112), described valve body and described secondary valve core (112) reset under the effect of described back-moving spring thus form list
To conducting oil circuit, so that the described hydraulic actuator of correspondence is by described one-way conduction oil circuit and described first working oil path
(2) the described one in and the second working oil path (3) connects, and described one-way conduction oil circuit is configured such that hydraulic oil can be from institute
State the described one in the first working oil path (2) and the second working oil path (3) and uniaxially flow to the hydraulic pressure execution of described correspondence
Element.
12. upper vehicle hydraulic systems according to claim 11, it is characterised in that described elastic spacing moment unit includes that
This connect stretching spring and push the ball, the two ends of this stretching spring are connected to described in the receiving of described one-way balance valve (11)
The valve body of one-level spool (111) and described push the ball on, the valve body of described one-level spool (111) is formed with backstop platform, so that working as
Described pushing the ball overcomes the elastic force of described stretching spring to promote described one-level spool (111) to drive described secondary valve core (112)
When arriving predetermined partial journey, described in push the ball by described backstop platform backstop, and described in push the ball and described backstop platform seal laminating
So that described one-level spool (111) is sealed in the valve body of described one-level spool (111).
13. upper vehicle hydraulic systems according to claim 11, it is characterised in that described one-way balance valve (11) includes respectively
The middle oil circuit of one-way balance valve the 3rd being connected with the hydraulic control end of described first working oil path (2) and described secondary valve core (112)
(115), this middle oil circuit of one-way balance valve the 3rd (115) is provided with the middle oil circuit check valve of one-way balance valve the 3rd (116),
The forward port of the described middle oil circuit check valve of one-way balance valve the 3rd (116) is connected to the hydraulic control of described secondary valve core (112)
End, reverse port is connected to described first working oil path (2).
14. upper vehicle hydraulic systems according to claim 11, it is characterised in that the spring cavity of described back-moving spring is connected to
Executive component connects oil circuit, and this executive component connects oil circuit and connects the hydraulic pressure execution of described one-way balance valve (11) and described correspondence
Element.
15. upper vehicle hydraulic systems according to claim 11, it is characterised in that hydraulic pressure described in described at least two performs unit
A hydraulic actuator in part is boom derricking cylinder (12), and described one-way balance valve (11) is arranged on and becomes with described jib
In described first working oil path that the rodless cavity of width oil cylinder (12) connects.
16. upper vehicle hydraulic systems according to any one of claim 1 to 7, it is characterised in that described at least two hydraulic pressure
A hydraulic actuator in executive component is rotation of rotary table motor (13), described main oil-feed oil circuit (4) and main oil return circuit
(5) it is connected to described rotation of rotary table motor (13) by pilot valve (14), the second reversal valve (15) and one-way damper valve (16)
Brake cylinder, after the pressure of the hydraulic oil of described main oil-feed oil circuit (4) can be reduced by described pilot valve (14), supply is the most described
Brake cylinder.
17. upper vehicle hydraulic systems according to any one of claim 1 to 7, it is characterised in that described first working oil path
(2) and the second working oil path (3) is connected to fuel tank by overflow working oil path (17) the most respectively.
18. upper vehicle hydraulic systems as claimed in any of claims 1 to 7, it is characterised in that described main oil-feed oil circuit
(4) main oil feed pump (18) and emergency pump (19) it are connected to.
19. 1 kinds of engineering machinery, it is characterised in that this engineering machinery includes according to described in any one in claim 1 to 18
Upper vehicle hydraulic system.
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| CN201410448213.0A CN104235102B (en) | 2014-09-04 | 2014-09-04 | Getting-on hydraulic system and engineering machinery |
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| CN201410448213.0A CN104235102B (en) | 2014-09-04 | 2014-09-04 | Getting-on hydraulic system and engineering machinery |
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| CN104235102A CN104235102A (en) | 2014-12-24 |
| CN104235102B true CN104235102B (en) | 2016-08-17 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN107989839A (en) * | 2017-11-23 | 2018-05-04 | 宁波文泽机电技术开发有限公司 | Two-way pressure-compensated valve |
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| CN106837906B (en) * | 2016-12-14 | 2018-07-06 | 武汉船用机械有限责任公司 | A kind of anchor capstan hydraulic control system |
| CN109723693B (en) * | 2019-01-15 | 2023-10-03 | 江苏徐工工程机械研究院有限公司 | Load-sensitive multi-way valve and hydraulic system |
| CN112065802B (en) * | 2020-09-29 | 2024-06-25 | 浙江海宏液压科技股份有限公司 | Hydraulic lifting system |
| CN112814961B (en) * | 2021-01-15 | 2023-05-30 | 三一汽车制造有限公司 | Boom hydraulic system of working vehicle, control method and working vehicle |
| CN113931893A (en) * | 2021-09-28 | 2022-01-14 | 中联重科股份有限公司 | Load-sensitive multi-way valve with independently controlled load port and hydraulic system |
| CN113931896B (en) * | 2021-09-28 | 2022-12-06 | 常德中联重科液压有限公司 | Sensitive multiple unit valve of load mouth independent control load and hydraulic system |
| CN114476947B (en) * | 2021-12-29 | 2023-07-07 | 中联重科股份有限公司 | Emergency hydraulic system and automobile crane |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JPS5656472U (en) * | 1979-10-09 | 1981-05-16 | ||
| US5699665A (en) * | 1996-04-10 | 1997-12-23 | Commercial Intertech Corp. | Control system with induced load isolation and relief |
| JPH11182674A (en) * | 1997-12-17 | 1999-07-06 | Komatsu Ltd | Device and method for controlling forward/backward switching of hydraulic driven vehicle |
| CN201144902Y (en) * | 2007-12-21 | 2008-11-05 | 沈阳矿山机械（集团）有限责任公司 | Hydraulic system for development machine |
| CN201613240U (en) * | 2009-12-09 | 2010-10-27 | 天津工程师范学院 | Crawler tank cleaning robot hydraulic system |
| CN202789786U (en) * | 2012-09-17 | 2013-03-13 | 中联重科股份有限公司 | Hydraulic system and concrete pump truck and engineering machinery comprising same |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107989839A (en) * | 2017-11-23 | 2018-05-04 | 宁波文泽机电技术开发有限公司 | Two-way pressure-compensated valve |
| CN107989839B (en) * | 2017-11-23 | 2019-12-24 | 江苏南京白马现代农业高新技术产业园有限公司 | Two-way pressure compensating valve |
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