CN105035979B - Balance valve group and hydraulic system - Google Patents
Balance valve group and hydraulic system Download PDFInfo
- Publication number
- CN105035979B CN105035979B CN201510473792.9A CN201510473792A CN105035979B CN 105035979 B CN105035979 B CN 105035979B CN 201510473792 A CN201510473792 A CN 201510473792A CN 105035979 B CN105035979 B CN 105035979B
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- valve
- pressure
- compensated
- actuator port
- balanced
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- 239000003921 oil Substances 0.000 claims abstract description 117
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 46
- 239000007788 liquid Substances 0.000 claims description 71
- 239000012530 fluid Substances 0.000 claims description 23
- 230000007704 transition Effects 0.000 claims description 22
- 238000013016 damping Methods 0.000 claims description 14
- 239000002828 fuel tank Substances 0.000 claims description 14
- 238000000034 method Methods 0.000 claims description 10
- 230000009467 reduction Effects 0.000 claims description 10
- 230000008569 process Effects 0.000 claims description 9
- 238000004146 energy storage Methods 0.000 claims description 8
- 238000005303 weighing Methods 0.000 claims description 8
- 238000007789 sealing Methods 0.000 claims description 6
- 238000004891 communication Methods 0.000 claims description 5
- 230000008901 benefit Effects 0.000 claims description 4
- 230000001419 dependent effect Effects 0.000 claims description 3
- 238000003780 insertion Methods 0.000 claims description 3
- 230000037431 insertion Effects 0.000 claims description 3
- 239000007853 buffer solution Substances 0.000 claims description 2
- 230000017105 transposition Effects 0.000 claims description 2
- 238000002955 isolation Methods 0.000 claims 1
- 238000010586 diagram Methods 0.000 description 7
- 230000007246 mechanism Effects 0.000 description 7
- 230000008859 change Effects 0.000 description 3
- 230000008676 import Effects 0.000 description 3
- 238000004458 analytical method Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 239000000446 fuel Substances 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
- B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
- B66C23/62—Constructional features or details
- B66C23/82—Luffing gear
- B66C23/821—Bracing equipment for booms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
- F15B13/0426—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with fluid-operated pilot valves, i.e. multiple stage valves
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a balance valve group and a hydraulic system, the balance valve group comprises a balance valve (100), the balance valve (100) is provided with a balance valve first working oil port (101) used for leading to a load, a balance valve second working oil port (102) used for leading to an oil source or an oil tank, and a balance valve hydraulic control cavity (103) and a balance valve spring cavity (104) which are respectively arranged at two ends of a valve core of the balance valve (100), wherein the balance valve group also comprises a pressure compensation device connected with the balance valve (100) so as to keep the pressure difference between the balance valve first working oil port (101) and the balance valve second working oil port (102) constant when hydraulic oil flows back to the oil tank after passing through the balance valve first working oil port (101) and the balance valve second working oil port (102) from the load in sequence, so that the flow of the hydraulic oil passing through the balance valve (100) is independent of the pressure of the load only depending on the position of the valve core of the balance valve .
Description
Technical field
The present invention relates to Hydraulic Elements, in particular it relates to a kind of balance valve group and hydraulic system.
Background technology
Balanced valve is the crucial Hydraulic Elements for controlling autocrane luffing action, and it is applied in jib lubbing mechanism hydraulic system
In ensureing jib lubbing mechanism even running.Fig. 1 shows a kind of schematic diagram of jib lubbing mechanism hydraulic system of the prior art, bag
The hydraulic cylinder 4 for supporting luffing arm support of annexation connection, balanced valve 100 and reversal valve 5 as illustrated are included, from Fig. 1
As can be seen that due to the corresponding balanced valve hydraulic control oil circuit 18 of balanced valve 100 it is identical with the rod chamber pressure of hydraulic cylinder 4, so liquid
Pressure change in the rod chamber of cylinder pressure 4 can directly affect the opening degree of balanced valve 100, and in luffing arm support (i.e. hydraulic pressure is declined
The piston rod of cylinder 4 is retracted) when affect, with the changes in amplitude of luffing arm support, the pressure of the hydraulic oil in the rodless cavity of hydraulic cylinder 4
Also can be continually changing, then luffing arm support decrease speed can be continually changing, so as to affect hydraulic cylinder 4 rod chamber pressure (i.e.
The control pressure of balanced valve 100), can so cause balanced valve 100 constantly to move, aperture area is continually changing, so as to luffing
The stability that arm support declines is affected.
Fig. 2 shows the schematic diagram of another kind of jib lubbing mechanism hydraulic system of the prior art, including connecting as illustrated
The hydraulic cylinder 4 for supporting luffing arm support, balanced valve 100 and reversal valve 5 that relation connects, two hydraulic control ends point of reversal valve 5
Be not connected with the first oil circuit control 5a and the second oil circuit control 5b, and, the corresponding balanced valve hydraulic control oil circuit 18 of balanced valve 100 with
Second oil circuit control 5b (second oil circuit control 5b is connected to control crank) connections of reversal valve 5, in the jib lubbing mechanism hydraulic pressure
In system, because the pressure size of balanced valve hydraulic control oil circuit 18 can be controlled (quite by changing the angle of control crank
Can be controlled by changing control crank in the orifice size of the valve element of balanced valve 100), so when luffing arm support declines (i.e.
The piston rod of hydraulic cylinder 4 is retracted) when, the changes in amplitude of luffing arm support or cause
The stress change of hydraulic cylinder 4, the pressure for causing the hydraulic oil in the rodless cavity of hydraulic cylinder 4 is continually changing, although flat
The valve element aperture of weighing apparatus valve 100 is certain, but due to before and after the restriction of balanced valve 100 pressure reduction be continually changing, luffing declines flow also not
Disconnected change, the i.e. retraction speed of hydraulic cylinder 4 is uncontrolled.
In consideration of it, be necessary to provide a kind of new balance valve group, to overcome or alleviated by drawbacks described above.
The content of the invention
It is an object of the invention to provide a kind of balance valve group, inlet outlet pressure differential and the balance of the balanced valve in the balance valve group
The load of valve connection is unrelated, is steady state value.
It is a further object to provide a kind of hydraulic system, the balanced valve that the hydraulic system is provided using the present invention
Group.
To achieve these goals, the present invention provides a kind of balance valve group, and the balance valve group includes balanced valve, the balance
Valve has for leading to the actuator port of balanced valve first of load, the actuator port of balanced valve second for leading to oil sources or fuel tank
And be located at the balanced valve liquid controling cavity at the valve element two ends of the balanced valve respectively and balance valve spring chamber, wherein, the balance valve group
Also include the pressure compensator being connected with the balanced valve, to pass sequentially through the balanced valve the from the load in hydraulic oil
When one actuator port and the actuator port of the balanced valve second further flow back to fuel tank, the actuator port of the balanced valve first and institute are made
State the pressure reduction between the actuator port of balanced valve second and keep constant, so as to only be depended on by the flow of the hydraulic oil of the balanced valve
It is unrelated with the pressure of the load in the position of the balance valve core.
Preferably, the pressure compensator includes：Pilot valve, the pilot valve has pilot valve oil-in, pilot valve
Oil-out and pilot valve liquid controling cavity and pilot valve spring cavity respectively positioned at the valve element two ends of the pilot valve are described passing through
Pilot valve liquid controling cavity and pilot valve spring cavity coordinate the control pilot valve oil-in and pilot valve oil-out on or off, pressure
Force compensating valve, the pressure-compensated valve has the actuator port of pressure-compensated valve first, the actuator port of pressure-compensated valve second and divides
Not Wei Yu the pressure-compensated valve valve element two ends pressure-compensated valve liquid controling cavity and pressure-compensated valve spring cavity so that institute can be passed through
State pressure-compensated valve liquid controling cavity and pressure-compensated valve spring cavity coordinates the control pressure-compensated valve transposition, wherein, the balance
The actuator port of valve first is connected with the pilot valve liquid controling cavity, the actuator port of the balanced valve second and the pressure-compensated valve liquid
The connection of control chamber, and the actuator port of the balanced valve second is via the first damping unit and the pilot valve oil-in, pilot valve bullet
Spring chamber connects with pressure-compensated valve spring cavity.
Preferably, the actuator port of the balanced valve first and the pressure-compensated valve the second actuator port one-way conduction, and
The direction of the one-way conduction allows the hydraulic oil of the actuator port of pressure-compensated valve second to flow to the work of the balanced valve first
Make hydraulic fluid port.
Preferably, be provided with the second damping unit in the balanced valve liquid controling cavity with can buffer solution force feed into described
To the active force of the valve element of the balanced valve during balanced valve liquid controling cavity.
Preferably, the balanced valve is bi-bit bi-pass balanced valve, and can be between throttle position and one-way flow position
Switching, in the throttle position, the actuator port of the balanced valve first is with the actuator port of the balanced valve second by the oil that throttles
Road connects, and in the one-way flow position, hydraulic oil can flow to the balanced valve the from the actuator port of the balanced valve second
One actuator port.
Preferably, the pressure-compensated valve is bi-bit bi-pass pressure-compensated valve, and can be in throttle position and rest position
Between switch, in the throttle position, the actuator port of the pressure-compensated valve first and the working oil of the pressure-compensated valve second
Mouth passes through the oil communication that throttles, in the rest position, the actuator port of the pressure-compensated valve first and the pressure-compensated valve
Second actuator port ends each other.
Preferably, the pressure-compensated valve is 3-position-3-way pressure-compensated valve, and the pressure-compensated valve is also mended with pressure
The actuator port of valve the 3rd is repaid, the 3-position-3-way pressure-compensated valve can be in the work of the hydraulic oil in the pressure-compensated valve liquid controling cavity
Second is in the presence of first position, the hydraulic oil and spring force in the pressure-compensated valve spring cavity with lower
Put, and the centre position being between the first position and the second place, in the first position, the pressure
The actuator port of recuperation valve first respectively with the actuator port of the pressure-compensated valve second and the working oil of the pressure-compensated valve the 3rd
Mouth connection, in the centre position, the actuator port of the pressure-compensated valve first and the actuator port of the pressure-compensated valve the 3rd
Connect and end with the actuator port of the pressure-compensated valve second, in the second place, the pressure-compensated valve first works
Hydraulic fluid port ends respectively with the actuator port of the pressure-compensated valve second and the actuator port of the pressure-compensated valve the 3rd.
Preferably, the balance valve group is that integral type balances valve group, and the integral type balance valve group includes valve body, the valve body
Inside includes the balance valve chamber of the valve element of the receiving balanced valve being sequentially communicated, the valve element of the receiving pressure-compensated valve
Guide's valve chamber of the valve element of pressure compensation valve chamber and the receiving pilot valve.
Preferably, the balance valve chamber includes the spaced balanced valve liquid controling cavity, the chamber of balanced valve first successively
With the chamber of balanced valve second, the end in the balanced valve liquid controling cavity of the valve element of the balanced valve is connected with piston, described
Piston is in sealing contact with the perisporium of the balanced valve liquid controling cavity so that the balanced valve liquid controling cavity is separated into into exocoel a and inner chamber b, institute
Exocoel a is stated for receiving the outer liquid oil-control road of the balanced valve, being provided with the piston connects the exocoel a and inner chamber b
Logical damping plug, the part in the inner chamber b of the valve element of the balanced valve is provided with balance valve core oil leak hole, described
Balance valve core oil leak hole is connected by the passage being formed in the valve element of the balanced valve with the balanced valve spring cavity.
Preferably, the chamber of the balanced valve second connects with the actuator port of the balanced valve first, the chamber of the balanced valve first
Connect with the actuator port of the balanced valve second, be provided with boss portion on the valve element of the balanced valve, the boss portion can be
When the valve element of the balanced valve is moved optionally with the chamber between the chamber of the balanced valve first and the chamber of the balanced valve second
Wall is in sealing contact or is spaced, so that the chamber of the balanced valve first communicates with each other or completely cut off with the chamber of the balanced valve second.
Preferably, the chamber of the balanced valve first is by the actuator port of the balanced valve second and the pressure compensation valve chamber
Connection, the valve element of the pressure-compensated valve have away form one another and first end by the insertion of pressure-compensated valve inner passage and
Second end, the first end surrounds the pressure towards the actuator port of the balanced valve second, second end with the valve body
Recuperation valve spring cavity.
Preferably, there is the pressure connected with the pressure-compensated valve inner passage to mend on the valve element of the pressure-compensated valve
The cinclides of valve first is repaid, the cinclides of the pressure-compensated valve first can be selected in the moving process of the valve element of the pressure-compensated valve
Property ground connect or end with the actuator port of the pressure-compensated valve second being formed on the valve body, and the pressure-compensated valve
First cinclides can in the moving process of the valve element of the pressure-compensated valve optionally be formed in the valve body
Middle transition chamber connects or ends, and the middle transition chamber is connected with the middle transition oil duct for being provided with check valve, and the list
Hydraulic oil is allowed to flow to the middle transition oil duct, the middle transition oil duct and the balance from the middle transition chamber to valve
The chamber of valve second connects.
Preferably, the actuator port of pressure-compensated valve the 3rd, the valve element of the pressure-compensated valve are also formed with the valve body
It is upper that there is the cinclides of pressure-compensated valve second connected with the pressure-compensated valve inner passage, the cinclides of the pressure-compensated valve second
Can in the moving process of the valve element of the pressure-compensated valve optionally with the actuator port of the pressure-compensated valve the 3rd connect
Logical or cut-off.
Preferably, the spaced pilot valve spring cavity, the chamber of pilot valve first, elder generation successively are formed with the valve body
The chamber of pilot valve second and the pilot valve liquid controling cavity, the pressure-compensated valve spring cavity is by the pilot valve oil-in and the elder generation
The chamber of pilot valve second connects, and the in the chamber of the pilot valve first first opening is formed with the valve element of the pilot valve and is located at
The second opening in the chamber of the pilot valve second, first opening is connected by pilot valve inner passage with the described second opening
Logical, the pilot valve inner passage also connect with the pilot valve spring cavity, and the pilot valve liquid controling cavity passes through valve inner the
One passage is connected with the middle transition oil duct, and the chamber of the pilot valve first is by the pilot valve oil-out and valve inner the
Two channel connections, the valve inner second channel is connected with the balanced valve liquid controling cavity.
Additionally, the present invention also provides a kind of hydraulic system, wherein, the hydraulic system includes flat described in above-mentioned technical proposal
Weighing apparatus valve group, hydraulic cylinder and reversal valve, the rod chamber of the hydraulic cylinder is connected to the of the reversal valve by the first working oil path
One actuator port, rodless cavity are connected to the actuator port of the balanced valve first, and the actuator port of the pressure-compensated valve second passes through
Second working oil path is connected to the second actuator port of the reversal valve, the oil-in and oil return opening of the reversal valve respectively with master
Oil-feed oil circuit and main oil return circuit connect, and the reversal valve at least allow hand over for make first actuator port with it is described enter
Hydraulic fluid port is connected and second actuator port is connected with the oil return opening, or makes first actuator port and the oil return
Mouth is connected and second actuator port is connected with the oil-in.
Preferably, two hydraulic control ends of the reversal valve respectively with the first hydraulic control oil circuit a for being connected to hydraulic control handle and
Two hydraulic control oil circuit b connect, and the balanced valve liquid controling cavity is connected by balanced valve hydraulic control oil circuit with the second hydraulic control oil circuit b, institute
State the hydraulic oil in the second hydraulic control oil circuit b and can control the reversal valve and commutate to the piston rod retraction movement for making the hydraulic cylinder
Working position.
Preferably, the pressure-compensated valve also has the actuator port of pressure-compensated valve the 3rd, and the pressure-compensated valve is extremely
Allow hand over less to make the actuator port of the pressure-compensated valve first connect with the actuator port of the pressure-compensated valve the 3rd, it is described
The actuator port of pressure-compensated valve the 3rd is connected to energy-storage module.
Preferably, the pressure-compensated valve is 3-position-3-way pressure-compensated valve, and the 3-position-3-way pressure-compensated valve can be
First position is in the presence of hydraulic oil in the pressure-compensated valve liquid controling cavity, in the pressure-compensated valve spring cavity
The second place, and the working position being between the first position and the second place are in the presence of hydraulic oil
Put, in the first position, the actuator port of the pressure-compensated valve first respectively with the actuator port of the pressure-compensated valve second
Connect with the actuator port of the pressure-compensated valve the 3rd, in the centre position, the actuator port of the pressure-compensated valve first with
The actuator port of the pressure-compensated valve the 3rd is connected and ended with the actuator port of the pressure-compensated valve second, in the second
Put, the actuator port of the pressure-compensated valve first respectively with the actuator port of the pressure-compensated valve second and the pressure-compensated valve
3rd actuator port ends.
Preferably, the energy-storage module includes accumulator, and the accumulator is connected to the hydraulic pressure system by overflow oil circuit
The fuel tank of system.
Preferably, the hydraulic system is the luffing range of cantilever support hydraulic system of engineering machinery, and the hydraulic cylinder is the engineering
The driving cylinder of the luffing arm support of machinery.
By above-mentioned technical proposal, because the balance valve group also includes that the pressure compensation being connected with the balanced valve is filled
Put, to pass sequentially through the actuator port of the balanced valve first and the actuator port of the balanced valve second from the load in hydraulic oil
And then when flowing back to fuel tank, keep the pressure reduction between the actuator port of the balanced valve first and the actuator port of the balanced valve second
It is constant so that by the flow of the hydraulic oil of the balanced valve be only dependent upon it is described balance valve core position and with the load
Pressure it is unrelated, so the balanced valve in the balance valve group import and export (when hydraulic oil flows to balanced valve by load, import and export
The respectively actuator port of balanced valve first and the actuator port of balanced valve second) load that connects with balanced valve of pressure reduction is unrelated, is permanent
Definite value, especially, when the balance valve group is applied in the luffing range of cantilever support hydraulic system of engineering machinery (such as crane), can be with
Arm support decrease speed is controlled by the valve core opening area of the devices such as operation handle manipulation balanced valve, so that under arm support is steady
Drop, this is because arm support decrease speed depends on the flow of the hydraulic oil for flowing through balanced valve, and flows through the hydraulic oil stream of balanced valve
Amount it is relevant with the valve core opening area of balanced valve and balanced valve inlet outlet pressure differential, if guarantee balanced valve inlet outlet pressure differential it is constant with
And the valve core opening constant area of balanced valve, you can ensure certain by the hydraulic fluid flow rate of balanced valve.
Other features and advantages of the present invention will be described in detail in subsequent specific embodiment part.
Description of the drawings
Accompanying drawing is, for providing a further understanding of the present invention, and to constitute the part of specification, with following tool
Body embodiment is used to explain the present invention together, but is not construed as limiting the invention.In the accompanying drawings：
Fig. 1 is a kind of schematic diagram of jib lubbing mechanism hydraulic system of the prior art.
Fig. 2 is the schematic diagram of another kind of jib lubbing mechanism hydraulic system of the prior art.
Fig. 3 is the schematic diagram of balance valve group according to the embodiment of the present invention.
Fig. 4 is a kind of sectional view of the balance valve group of specific embodiment of the invention.
Fig. 5 is the sectional view of the balance valve group of another kind of specific embodiment of the invention.
Fig. 6 is a kind of schematic diagram of the hydraulic system of specific embodiment of the invention.
Fig. 7 is the schematic diagram of the hydraulic system of another kind of specific embodiment of the invention.
Description of reference numerals
The damping unit of 1 first damping unit 2 second
The hydraulic cylinder of 3 check valve 4
The working oil path of 5 reversal valve 6 first
The middle oil circuit of 7 second working oil path 8 first
The middle oil circuit of 9 draining oil circuit 10 second
The hydraulic pump of 11 the 3rd middle oil circuit 12
The main oil return circuit of 13 main oil-feed oil circuit 14
The overflow oil circuit of 15 accumulator 16
The balanced valve hydraulic control oil circuit of 17 overflow valve 18
5a the first oil circuit control the second oil circuit controls of 5b
The actuator port of 51 first actuator port 52 second
The first actuator port of balanced valve of 100 balanced valve 101
The balanced valve liquid controling cavity of 102 the second actuator port of balanced valve 103
103a exocoel 103b inner chambers
The first chamber of balanced valve of 104 balanced valve spring cavity 105
The piston of 106 the second chamber of balanced valve 107
The boss portion of 108 balance valve core oil leak hole 109
The pilot valve of 110 drain tap 200
The pilot valve oil-out of 201 pilot valve oil-in 202
The pilot valve spring cavity of 203 pilot valve liquid controling cavity 204
The second chamber of pilot valve of 205 the first chamber of pilot valve 206
207 first openings 208 second are open
The first actuator port of pressure-compensated valve of 300 pressure-compensated valve 301
The pressure-compensated valve liquid controling cavity of 302 the second actuator port of pressure-compensated valve 303
The actuator port of 304 pressure-compensated valve spring cavity, 305 pressure-compensated valve the 3rd
The first cinclides of pressure-compensated valve of 306 pressure compensation valve spring 307
The valve body of 308 the second cinclides of pressure-compensated valve 400
The middle transition oil duct of 401 middle transition chamber 402
The valve inner second channel of 403 valve inner first passage 404
The external passage of 405 external hydraulic fluid port 406
The valve pocket hole of 407 valve pocket 408
Specific embodiment
The specific embodiment of the present invention is described in detail below in conjunction with accompanying drawing.It should be appreciated that this place is retouched
The specific embodiment stated is merely to illustrate and explains the present invention, is not limited to the present invention.
Referring to Fig. 3, according to an aspect of the invention, there is provided a kind of balance valve group, the balance valve group includes balanced valve
100, balanced valve 100 has for leading to first actuator port of balanced valve 101 of load, the balance for leading to oil sources or fuel tank
The second actuator port of valve 102 and respectively positioned at the balanced valve 100 valve element two ends balanced valve liquid controling cavity 103 and balanced valve bullet
Spring chamber 104 be replaced with controlling balanced valve 100 by balanced valve liquid controling cavity 103 and the cooperation of balance valve spring chamber 104, wherein,
Balance valve group also includes the pressure compensator that is connected with balanced valve 100, to pass sequentially through balanced valve the from load in hydraulic oil
When one actuator port 101 and the second actuator port of balanced valve 102 further flow back to fuel tank, the He of the first actuator port of balanced valve 101 is made
Pressure reduction between the second actuator port of balanced valve 102 keeps constant, so as to only be depended on by the flow of the hydraulic oil of balanced valve 100
It is unrelated with the pressure of load in the position of balance valve core.
As noted previously, as balance valve group also includes the pressure compensator that is connected with balanced valve 100, with hydraulic oil from
When load passes sequentially through the first actuator port of balanced valve 101 and the second actuator port of balanced valve 102 and then flows back to fuel tank, balance is made
Pressure reduction between the first actuator port of valve 101 and the second actuator port of balanced valve 102 keeps constant, so as to pass through balanced valve 100
The flow of hydraulic oil be only dependent upon the position of balance valve core and unrelated with the pressure of load, so flat in the balance valve group
The import and export of weighing apparatus valve 100 (when hydraulic oil flows to balanced valve 100 by load, are imported and exported and are respectively the actuator port of balanced valve first
101 and the actuator port 102 of balanced valve second) load that connects with balanced valve 100 of pressure reduction is unrelated, is steady state value, especially, when this
When balance valve group is applied in the luffing range of cantilever support hydraulic system of engineering machinery (such as crane), can be by the dress such as operation handle
The valve core opening area for manipulating balanced valve 100 is put controlling arm support decrease speed, so that arm support steadily declines, this is because arm
Frame decrease speed depends on the flow of the hydraulic oil for flowing through balanced valve 100, and flows through the hydraulic fluid flow rate and balance of balanced valve 100
The valve core opening area of valve 100 is relevant with balanced valve inlet outlet pressure differential, if ensureing that balanced valve inlet outlet pressure differential is constant and flat
The valve core opening constant area of weighing apparatus valve, you can ensure certain by the hydraulic fluid flow rate of balanced valve 100.
Preferred embodiment of the invention, pressure compensator can include：Pilot valve 200, pilot valve 200 has
Pilot valve oil-in 201, pilot valve oil-out 202 and respectively positioned at the pilot valve 200 valve element two ends pilot valve liquid controling cavity
203 and pilot valve spring cavity 204 so that control pilot valve can be coordinated by pilot valve liquid controling cavity 203 and pilot valve spring cavity 204
Oil-in 201 and the on or off of pilot valve oil-out 202, pressure-compensated valve 300, pressure-compensated valve 300 has pressure compensation
The first actuator port of valve 301, the second actuator port of pressure-compensated valve 302 and respectively positioned at the pressure-compensated valve 300 valve element two
The pressure-compensated valve liquid controling cavity 303 and pressure-compensated valve spring cavity 304 at end with can by pressure-compensated valve liquid controling cavity 303 and pressure
Force compensating valve spring chamber 304 coordinates control pressure recuperation valve 300 to replace, wherein, the first actuator port of balanced valve 101 and pilot valve
Liquid controling cavity 203 is connected, and the second actuator port of balanced valve 102 is connected with pressure-compensated valve liquid controling cavity 303, and balanced valve second works
Hydraulic fluid port 102 is via the first damping unit 1 and pilot valve oil-in 201, pilot valve spring cavity 204 and pressure-compensated valve spring cavity
304 connections.
It is the balanced valve for how ensureing balanced valve 100 to make a concrete analysis of the balance valve group in above-mentioned preferred embodiment below
Pressure reduction is constant between one actuator port 101 and the second actuator port of balanced valve 102：
Assume that the first actuator port of balanced valve 101 is connected by the first middle oil circuit 8 with pilot valve liquid controling cavity 203, balance
The second actuator port of valve 102 is connected by the second middle oil circuit 10 with pressure-compensated valve liquid controling cavity 303, the working oil of balanced valve second
After mouthfuls 102 via the first damping unit 1, then via after the 3rd middle oil circuit 11 with pilot valve oil-in 201 and pressure compensation
Valve spring chamber 304 connects, and with reference to Fig. 3 analyses, the hydraulic fluid pressure at the first actuator port of balanced valve 101 is Pb, balanced valve
Hydraulic fluid pressure at second actuator port 102 is Pa, the hydraulic fluid pressure on the 3rd middle oil circuit 11 is Pc, pressure-compensated valve
When the spring force of spring cavity 304 is f1, the spring force of pilot valve spring cavity 204 is f2, the hydraulic connecting relation in figure can
To be easy to draw the hydraulic fluid pressure=Pb on the middle oil circuit 8 of hydraulic fluid pressure=the first in pilot valve liquid controling cavity 203, pressure
Hydraulic fluid pressure=Pa on the middle oil circuit 10 of hydraulic fluid pressure=the second of force compensating valve liquid controling cavity 303, and guide's valve spring
Hydraulic fluid pressure in chamber 204 and pressure-compensated valve spring cavity 304 is respectively equal to the hydraulic oil pressure on the 3rd middle oil circuit 11
Power Pc, when pilot valve 200 and pressure-compensated valve 300 respectively reach dynamic equilibrium, there is Pb=Pc+f2；Pa=Pc+f1, so as to
Pb-Pa=f2-f1, that is to say, that the pressure reduction between the first actuator port of balanced valve 101 and the second actuator port of balanced valve 102
Determined by the difference of the spring force in the spring force in pilot valve 200 and pressure-compensated valve 300, as long as have selected pilot valve 200
With pressure-compensated valve 300, this difference is steady state value.
Additionally, the first actuator port of balanced valve 101 can with the one-way conduction of the second actuator port of pressure-compensated valve 302, and
The direction of one-way conduction allows the hydraulic oil of the second actuator port of pressure-compensated valve 302 to flow to the first actuator port of balanced valve 101,
Specifically, the first actuator port of balanced valve 101 can be provided by the oil circuit and the working oil of pressure-compensated valve second of check valve 3
Mouthful 302 one-way conductions, can so make a part of unnecessary running of hydraulic power oil at the second actuator port of pressure-compensated valve 302 to flat
The first actuator port of weighing apparatus valve 101, when the balance valve group is applied to the luffing range of cantilever support hydraulic system of engineering machinery (such as crane)
When middle, the first actuator port of balanced valve 101 can be connected to the rodless cavity of the driving cylinder of arm support, so the work of pressure-compensated valve second
Make a part of unnecessary running of hydraulic power oil to the first actuator port of balanced valve 101 at hydraulic fluid port 302 can be used for it is (right to arm support raising
Should stretch out in the piston rod of driving cylinder) fuel feeding.
Preferably, the second damping unit 2 (can be damping plug etc.) is provided with balanced valve liquid controling cavity 103 buffering
Hydraulic oil is during into balanced valve liquid controling cavity 103 to the active force of the valve element of balanced valve 100.
In addition, balanced valve spring cavity 104, pilot valve oil-out 202 may also connect to draining oil circuit 9, the draining oil circuit 9
For connecting fuel tank so that the unnecessary hydraulic oil of balanced valve spring cavity 104 and pilot valve oil-out 202 is discharged.
From figure 3, it can be seen that balanced valve 100 be preferably bi-bit bi-pass balanced valve, and can throttle position with it is unidirectional
Switch between flow locations, in throttle position, the first actuator port of balanced valve 101 passes through with the second actuator port of balanced valve 102
Throttling oil communication, in one-way flow position, hydraulic oil can flow to the work of balanced valve first from the second actuator port of balanced valve 102
Make hydraulic fluid port 101, but balanced valve 100 is clearly not limited to bi-bit bi-pass balanced valve.
In addition, pressure-compensated valve 300 is preferably bi-bit bi-pass pressure-compensated valve, and can be in throttle position and rest position
Between switch, in throttle position, the first actuator port of pressure-compensated valve 301 passes through with the second actuator port of pressure-compensated valve 302
Throttling oil communication, in rest position, the first actuator port of pressure-compensated valve 301 and the second actuator port of pressure-compensated valve 302
End each other, but pressure-compensated valve 300 is clearly not limited to bi-bit bi-pass pressure-compensated valve, for example, pressure-compensated valve 300 may be used also
To be 3-position-3-way pressure-compensated valve, pressure-compensated valve 300 can also be with the actuator port 305 of pressure-compensated valve the 3rd, and this three
Position three-way pressure compensating valve can be in first position in the presence of the hydraulic oil in pressure-compensated valve liquid controling cavity 303, in pressure
The second place is in the presence of hydraulic oil and spring force in force compensating valve spring chamber 304, and is at first position
Centre position between the second place, in first position, the first actuator port of pressure-compensated valve 301 respectively with pressure-compensated valve
Second actuator port 302 is connected with the actuator port 305 of pressure-compensated valve the 3rd, and in centre position, pressure-compensated valve first works
Hydraulic fluid port 301 is connected with the actuator port 305 of pressure-compensated valve the 3rd and ended with the second actuator port of pressure-compensated valve 302,
Two positions, the first actuator port of pressure-compensated valve 301 respectively with the second actuator port of pressure-compensated valve 302 and pressure-compensated valve
Three actuator ports 305 end.
Referring to Fig. 4 and Fig. 5, balance valve group can balance valve group for integral type, and the integral type balance valve group can include valve
Body 400, the inside of valve body 400 includes the balance valve chamber of the valve element of the receiving balanced valve 100 being sequentially communicated, accommodates pressure-compensated valve
Guide's valve chamber of the pressure compensation valve chamber of 300 valve element and the valve element of receiving pilot valve 200.
Referring to Fig. 4, a kind of specific embodiment of the invention, balance valve chamber can include spaced successively
Balanced valve liquid controling cavity 103, the first chamber of balanced valve 105 and the second chamber of balanced valve 106, the valve element of balanced valve 100 positioned at balanced valve
The perisporium that end in liquid controling cavity 103 is connected with piston 107, piston 107 and balanced valve liquid controling cavity 103 is in sealing contact balancing
Valve liquid controling cavity 103 is separated into exocoel 103a and inner chamber 103b, and exocoel 103a is used for the outer liquid oil-control road of receiving balance valve 100,
For example balanced valve hydraulic control oil circuit 18 is connected to by the external passage 406 on a valve gap, being provided with piston 107 makes exocoel
103a and the damping plug (the second damping unit 2 i.e. above-mentioned) that inner chamber 103b is connected, the valve element of balanced valve 100 positioned at interior
Part in the 103b of chamber is provided with balance valve core oil leak hole 108, and balance valve core oil leak hole 108 is by being formed in balanced valve
The interior passage of 100 valve element is connected with balanced valve spring cavity 104, balanced valve spring cavity 104 can with another valve gap on
External hydraulic fluid port 405 connects, and the external hydraulic fluid port 405 is used to be connected for draining with fuel tank.
In addition, the second chamber of balanced valve 106 connects with the first actuator port of balanced valve 101, the first chamber of balanced valve 105 and balance
The second actuator port of valve 102 is connected, and boss portion 109 is provided with the valve element of balanced valve 100, and boss portion 109 can be in balanced valve
100 valve element is optionally in sealing contact with the chamber wall between the first chamber of balanced valve 105 and the second chamber of balanced valve 106 when moving
Or interval, so that the first chamber of balanced valve 105 communicates with each other or completely cuts off with the second chamber of balanced valve 106.The first chamber of balanced valve 105 can be with
By the second actuator port of balanced valve 102 and pressure-compensated valve chamber, the valve element of pressure-compensated valve 300 has away form one another
And the first end by the insertion of pressure-compensated valve inner passage and the second end, first end is towards the actuator port of balanced valve second
102, the second end surrounds pressure-compensated valve spring cavity 304 with valve body 400.
Additionally, having the pressure-compensated valve the connected with pressure-compensated valve inner passage on the valve element of pressure-compensated valve 300
One cinclides 307, the first cinclides of pressure-compensated valve 307 can be in the moving process of the valve element of pressure-compensated valve 300 optionally
Connected with the second actuator port of pressure-compensated valve 302 being formed on valve body 400 by the valve pocket hole 408 on valve pocket 407 or cut
Only, and the first cinclides of pressure-compensated valve 307 can in the moving process of the valve element of pressure-compensated valve 300 optionally through
Valve pocket hole 408 on valve pocket 407 connects or ends with the middle transition chamber 401 being formed in valve body 400, middle transition chamber 401
It is connected with the middle transition oil duct 402 for being provided with check valve 3, and during check valve 3 allows hydraulic oil to flow to from middle adapter cavity 401
Between transition oil duct 402, middle transition oil duct 402 connects with the second chamber of balanced valve 106.
Preferably, referring to Fig. 5, the actuator port 305 of pressure-compensated valve the 3rd can be also formed with valve body 400, pressure is mended
Repay and there is the second cinclides of pressure-compensated valve 308 connected with pressure-compensated valve inner passage, pressure-compensated valve on the valve element of valve 300
Second cinclides 308 can in the moving process of the valve element of pressure-compensated valve 300 optionally with pressure-compensated valve the 3rd work
Hydraulic fluid port 305 is connected or ended.
Additionally, could be formed with spaced pilot valve spring cavity 204, the chamber of pilot valve first successively in valve body 400
205th, the second chamber of pilot valve 206 and pilot valve liquid controling cavity 203, pressure-compensated valve spring cavity 304 can pass through pilot valve oil-in
201 connect with the second chamber of pilot valve 206, and in the first chamber of pilot valve 205 is could be formed with the valve element of pilot valve 200
One opening 207 and in the second chamber of pilot valve 206 second opening 208, first opening 207 by pilot valve inner passage with
Second opening 208 is connected, and pilot valve inner passage also connects with pilot valve spring cavity 204, and pilot valve liquid controling cavity 203 passes through valve body
Inside first channel 403 is connected with middle transition oil duct 402, and the first chamber of pilot valve 205 is by pilot valve oil-out 202 and valve body
Internal second channel 404 is connected, and valve inner second channel 404 is connected with balanced valve liquid controling cavity 103.
From figure 5 it can be seen that another kind of specific embodiment of the invention, could be formed with valve body 400 with
The drain tap 110 of the connection of balanced valve liquid controling cavity 103, drain tap 110 is used to connect fuel tank, lets out such that it is able to pass through drain tap 110
Fall the unnecessary hydraulic oil in balanced valve liquid controling cavity 103, and, when pilot valve 200 is opened, the hydraulic oil in pilot valve 200
Balanced valve liquid controling cavity 103 can be reached by way of valve inner second channel 404, and then fuel tank is flow back into by drain tap 110.
Referring to Fig. 6 and Fig. 7, according to another aspect of the present invention, there is provided a kind of hydraulic system, wherein, the hydraulic system
Including above-mentioned balance valve group, hydraulic cylinder 4 and reversal valve 5, the rod chamber of hydraulic cylinder 4 is connected to commutation by the first working oil path 6
First actuator port 51, rodless cavity of valve 5 is connected to the first actuator port of balanced valve 101, the actuator port of pressure-compensated valve second
302 the second actuator ports 52 that reversal valve 5 is connected to by the second working oil path 7, the oil-in 53 and oil return opening 54 of reversal valve 5
It is connected with main oil-feed oil circuit 13 and main oil return circuit 14 respectively, and reversal valve 5 is at least allowed hand over to make the first actuator port 51
Connect with oil-in and the second actuator port 52 is connected with oil return opening, or the first actuator port 51 is connected simultaneously with oil return opening
And second actuator port 52 connect with oil-in.Because the hydraulic system includes above-mentioned balanced valve, so being based on above-mentioned balanced valve
Advantage understand, will be more steady when the piston rod of hydraulic cylinder 4 is retracted, and speed is controllable.
Specifically, two hydraulic control ends of reversal valve 5 can respectively with the first hydraulic control oil circuit 5a for being connected to hydraulic control handle and
Second hydraulic control oil circuit 5b connects, and balanced valve liquid controling cavity 103 is connected by balanced valve hydraulic control oil circuit 18 with the second hydraulic control oil circuit 5b, the
Hydraulic oil in two hydraulic control oil circuit 5b can control reversal valve 5 and commutate to the working position of the piston rod retraction movement for making hydraulic cylinder 4,
So the retraction speed of the piston rod of hydraulic cylinder 4 can be controlled by operating hydraulic control handle.
Above-mentioned hydraulic system is preferably the luffing range of cantilever support hydraulic system of engineering machinery, and hydraulic cylinder 4 can be engineering machinery
The driving cylinder of the luffing arm support of (such as crane), due to having been mentioned above when the balance valve group is applied to engineering machinery
When in luffing range of cantilever support hydraulic system, can be controlled by the valve core opening area of the devices such as operation handle manipulation balanced valve 100
Arm support decrease speed, so that arm support steadily declines.Here no longer repeat specification is carried out to these advantages.
Additionally, the actuator port 305 of pressure-compensated valve the 3rd can be connected to energy-storage module, so as in pressure-compensated valve first
When actuator port 301 is connected with the actuator port 305 of pressure-compensated valve the 3rd, by a part of hydraulic pressure in the rodless cavity of hydraulic cylinder 4
Oil is stored to energy-storage module.
The particular type of energy-storage module is simultaneously not particularly limited, and for example, energy-storage module can include accumulator 15, accumulation of energy
Device 15 can be provided by the fuel tank that the overflow oil circuit 16 of overflow valve 17 is connected to hydraulic system.
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
The detail in mode is applied, in the range of the technology design of the present invention, various letters can be carried out to technical scheme
Monotropic type, these simple variants belong to protection scope of the present invention.
It is further to note that each particular technique feature described in above-mentioned specific embodiment, in not lance
In the case of shield, can be combined by any suitable means.In order to avoid unnecessary repetition, the present invention to it is various can
The combination of energy is no longer separately illustrated.
Additionally, can also be combined between a variety of embodiments of the present invention, as long as it is without prejudice to this
The thought of invention, it should equally be considered as content disclosed in this invention.
Claims (19)
1. valve group balanced, the balance valve group includes balanced valve (100), the balanced valve (100) is with for leading to the flat of load
The weighing apparatus actuator port of valve first (101), the actuator port of the balanced valve second (102) for leading to fuel tank and respectively positioned at the balance
The balanced valve liquid controling cavity (103) and balance valve spring chamber (104) at the valve element two ends of valve (100), it is characterised in that
The balance valve group also includes the pressure compensator being connected with the balanced valve (100), to bear from described in hydraulic oil
Load passes sequentially through the actuator port of the balanced valve first (101) and the actuator port of the balanced valve second (102) and then flows back to oil
During case, keep the pressure reduction between the actuator port of the balanced valve first (101) and the actuator port of the balanced valve second (102)
It is constant so that by the flow of the hydraulic oil of the balanced valve (100) be only dependent upon it is described balance valve core position and with institute
The pressure for stating load is unrelated,
Wherein, the pressure compensator includes：
Pilot valve (200), the pilot valve (200) is with pilot valve oil-in (201), pilot valve oil-out (202) and difference
Positioned at the pilot valve liquid controling cavity (203) and pilot valve spring cavity (204) at the valve element two ends of the pilot valve (200) so that institute can be passed through
State pilot valve liquid controling cavity (203) and pilot valve spring cavity (204) coordinates the control pilot valve oil-in (201) to go out with pilot valve
Hydraulic fluid port (202) on or off,
Pressure-compensated valve (300), the pressure-compensated valve (300) is mended with the actuator port of pressure-compensated valve first (301), pressure
Repay the actuator port of valve second (302) and respectively positioned at the pressure-compensated valve liquid controling cavity at the valve element two ends of the pressure-compensated valve (300)
And pressure-compensated valve spring cavity (304) is with can be by the pressure-compensated valve liquid controling cavity (303) and pressure-compensated valve bullet (303)
Spring chamber (304) coordinates control pressure-compensated valve (300) transposition,
Wherein, the actuator port of the balanced valve first (101) is connected with the pilot valve liquid controling cavity (203), the balanced valve
Two actuator ports (102) are connected with the pressure-compensated valve liquid controling cavity (303), and the actuator port of the balanced valve second (102)
Via the first damping unit (1) and the pilot valve oil-in (201), pilot valve spring cavity (204) and pressure compensation valve spring
Chamber (304) connects.
2. balance valve group according to claim 1, it is characterised in that the actuator port of the balanced valve first (101) and institute
Actuator port (302) one-way conduction of pressure-compensated valve second is stated, and the direction of the one-way conduction allows the pressure-compensated valve
The hydraulic oil of the second actuator port (302) flows to the actuator port of the balanced valve first (101).
3. balance valve group according to claim 1, it is characterised in that is provided with the balanced valve liquid controling cavity (103)
Two damping units (2) with can buffer solution force feed during into the balanced valve liquid controling cavity (103) to the balanced valve
(100) active force of valve element.
4. balance valve group as claimed in any of claims 1 to 3, it is characterised in that the balanced valve (100) is two
Position two-way balanced valve, and can switch between throttle position and one-way flow position, in the throttle position, the balanced valve
First actuator port (101) and the actuator port of the balanced valve second (102) by the oil communication that throttles, in the one-way flow
Position, hydraulic oil can flow to the actuator port of the balanced valve first (101) from the actuator port of the balanced valve second (102).
5. balance valve group as claimed in any of claims 1 to 3, it is characterised in that the pressure-compensated valve (300)
For bi-bit bi-pass pressure-compensated valve, and can switch between throttle position and rest position, in the throttle position, the pressure
The actuator port of force compensating valve first (301) and the actuator port of the pressure-compensated valve second (302) by the oil communication that throttles,
The rest position, the actuator port of the pressure-compensated valve first (301) and the actuator port of the pressure-compensated valve second (302)
End each other.
6. balance valve group as claimed in any of claims 1 to 3, it is characterised in that the pressure-compensated valve (300)
For 3-position-3-way pressure-compensated valve, the pressure-compensated valve (300), should also with the actuator port (305) of pressure-compensated valve the 3rd
3-position-3-way pressure-compensated valve can be in first in the presence of the hydraulic oil in the pressure-compensated valve liquid controling cavity (303)
Put, the second place is in the presence of the hydraulic oil and spring force in the pressure-compensated valve spring cavity (304), and can locate
Centre position between the first position and the second place, in the first position, the pressure-compensated valve first
Actuator port (301) respectively with the actuator port of the pressure-compensated valve second (302) and the working oil of the pressure-compensated valve the 3rd
Mouthful (305) connection, in the centre position, the actuator port of the pressure-compensated valve first (301) and the pressure-compensated valve the
Three actuator ports (305) are connected and ended with the actuator port of the pressure-compensated valve second (302), in the second place, institute
State the actuator port of pressure-compensated valve first (301) respectively with the actuator port of the pressure-compensated valve second (302) and the pressure
The actuator port (305) of recuperation valve the 3rd ends.
7. balance valve group as claimed in any of claims 1 to 3, it is characterised in that the balance valve group is integrated
Formula balances valve group, and the integral type balance valve group includes valve body (400), and the receiving being sequentially communicated is included inside the valve body (400)
The balance valve chamber of the valve element of the balanced valve (100), the pressure compensation valve pocket of the valve element of the receiving pressure-compensated valve (300)
Guide's valve chamber of the valve element of room and the receiving pilot valve (200).
8. balance valve group according to claim 7, it is characterised in that the balance valve chamber includes spaced successively
The balanced valve liquid controling cavity (103), the chamber of balanced valve first (105) and the chamber of balanced valve second (106), the balanced valve (100)
The end in the balanced valve liquid controling cavity (103) of valve element is connected with piston (107), and the piston (107) is flat with described
The perisporium of weighing apparatus valve liquid controling cavity (103) is in sealing contact so that the balanced valve liquid controling cavity (103) is separated into into exocoel (103a) and inner chamber
(103b), the exocoel (103a) is used to receive the outer liquid oil-control road of the balanced valve (100), sets on the piston (107)
Be equipped with the damping plug for making the exocoel (103a) connect with inner chamber (103b), the valve element of the balanced valve (100) positioned at described
Part in inner chamber (103b) is provided with balance valve core oil leak hole (108), and balance valve core oil leak hole (108) is by shape
Connect with the balanced valve spring cavity (104) into the passage in the valve element in the balanced valve (100).
9. balance valve group according to claim 8, it is characterised in that the chamber of the balanced valve second (106) and the balance
The actuator port of valve first (101) is connected, and the chamber of the balanced valve first (105) is with the actuator port of the balanced valve second (102) even
It is logical, boss portion (109) is provided with the valve element of the balanced valve (100), the boss portion (109) can be in the balanced valve
(100) when valve element is moved optionally between the chamber of the balanced valve first (105) and the chamber of the balanced valve second (106)
Chamber wall is in sealing contact or is spaced, so that the chamber of the balanced valve first (105) communicates with each other with the chamber of the balanced valve second (106)
Or isolation.
10. balance valve group according to claim 9, it is characterised in that the chamber of the balanced valve first (105) is by described flat
The weighing apparatus actuator port of valve second (102) and the pressure-compensated valve chamber, the valve element of the pressure-compensated valve (300) has that
This back to and the first end by the insertion of pressure-compensated valve inner passage and the second end, the first end is towards the balanced valve
Second actuator port (102), second end surrounds the pressure-compensated valve spring cavity (304) with the valve body (400).
11. balance valve groups according to claim 10, it is characterised in that have on the valve element of the pressure-compensated valve (300)
There are the cinclides of the pressure-compensated valve first (307) connected with the pressure-compensated valve inner passage, the wall of the pressure-compensated valve first
Hole (307) can in the moving process of the valve element of the pressure-compensated valve (300) optionally be formed in the valve body
(400) actuator port of the pressure-compensated valve second (302) connection or cut-off on, and the cinclides of the pressure-compensated valve first
(307) can in the moving process of the valve element of the pressure-compensated valve (300) optionally be formed in the valve body
(400) middle transition chamber (401) connection or cut-off, the middle transition chamber (401) and the centre for being provided with check valve (3) in
Transition oil duct (402) connects, and the check valve (3) allows hydraulic oil to flow to the centre from the middle transition chamber (401)
Transition oil duct (402), the middle transition oil duct (402) connects with the chamber of the balanced valve second (106).
12. balance valve groups according to claim 11, it is characterised in that pressure benefit is also formed with the valve body (400)
The actuator port (305) of valve the 3rd is repaid, is had and the pressure-compensated valve inner passage on the valve element of the pressure-compensated valve (300)
The cinclides of the pressure-compensated valve second (308) of connection, the cinclides of the pressure-compensated valve second (308) can be in the pressure-compensated valve
(300) optionally with the actuator port (305) of the pressure-compensated valve the 3rd connect or end in the moving process of valve element.
13. balance valve groups according to claim 11, it is characterised in that be formed with the valve body (400) and be spaced successively
The pilot valve spring cavity (204), the chamber of pilot valve first (205), the chamber of pilot valve second (206) and the pilot valve liquid for arranging
Control chamber (203), the pressure-compensated valve spring cavity (304) is by the pilot valve oil-in (201) and the pilot valve second
Chamber (206) connects, and first be formed with the chamber of the pilot valve first (205) on the valve element of the pilot valve (200) opens
Mouth (207) and the second opening (208) in the chamber of the pilot valve second (206), first opening (207) is by guide
Valve inner passage with described second opening (208) connect, the pilot valve inner passage also with the pilot valve spring cavity (204)
Connection, the pilot valve liquid controling cavity (203) is connected by valve inner first passage (403) with the middle transition oil duct (402)
Logical, the chamber of the pilot valve first (205) is connected by the pilot valve oil-out (202) with valve inner second channel (404),
The valve inner second channel (404) connects with the balanced valve liquid controling cavity (103).
14. a kind of hydraulic systems, it is characterised in that the hydraulic system includes as claimed in any of claims 1 to 3
Balance valve group, hydraulic cylinder (4) and reversal valve (5), the rod chamber of the hydraulic cylinder (4) is connected to by the first working oil path (6)
First actuator port (51) of the reversal valve (5), rodless cavity are connected to the actuator port of the balanced valve first (101), described
The actuator port of pressure-compensated valve second (302) is connected to the second working oil of the reversal valve (5) by the second working oil path (7)
Mouth (52), the oil-in and oil return opening of the reversal valve (5) are connected respectively with main oil-feed oil circuit (13) and main oil return circuit (14),
And the reversal valve (5) is at least allowed hand over to make first actuator port (51) connect with the oil-in and described
Two actuator ports (52) are connected with the oil return opening, or first actuator port (51) is connected with the oil return opening and
Second actuator port (52) connects with the oil-in.
15. hydraulic systems according to claim 14, it is characterised in that two hydraulic control ends difference of the reversal valve (5)
It is connected with the first hydraulic control oil circuit (5a) and the second hydraulic control oil circuit (5b) that are connected to hydraulic control handle, the balanced valve liquid controling cavity
(103) it is connected with the second hydraulic control oil circuit (5b) by balanced valve hydraulic control oil circuit (18), in the second hydraulic control oil circuit (5b)
Hydraulic oil can control the reversal valve (5) and commutate to the working position of the piston rod retraction movement for making the hydraulic cylinder (4).
16. hydraulic systems according to claim 14, it is characterised in that the pressure-compensated valve (300) also has pressure
The actuator port (305) of recuperation valve the 3rd, and the pressure-compensated valve (300) at least allowed hand over to make the pressure-compensated valve
One actuator port (301) is connected with the actuator port (305) of the pressure-compensated valve the 3rd, the working oil of the pressure-compensated valve the 3rd
Mouth (305) is connected to energy-storage module.
17. hydraulic systems according to claim 16, it is characterised in that the pressure-compensated valve (300) is 3-position-3-way
Pressure-compensated valve, the 3-position-3-way pressure-compensated valve can be in the work of the hydraulic oil in the pressure-compensated valve liquid controling cavity (303)
With it is lower in the presence of first position, the hydraulic oil in the pressure-compensated valve spring cavity (304) be in the second place, and
The centre position being between the first position and the second place, in the first position, the pressure compensation
The actuator port of valve first (301) respectively with the actuator port of the pressure-compensated valve second (302) and the pressure-compensated valve the 3rd
Actuator port (305) is connected, and in the centre position, the actuator port of the pressure-compensated valve first (301) is mended with the pressure
Repay the connection of the actuator port (305) of valve the 3rd and end with the actuator port of the pressure-compensated valve second (302), in the second
Put, the actuator port of the pressure-compensated valve first (301) respectively with the actuator port of the pressure-compensated valve second (302) and described
The actuator port (305) of pressure-compensated valve the 3rd ends.
18. hydraulic systems according to claim 16, it is characterised in that the energy-storage module includes accumulator (15), institute
State the fuel tank that accumulator (15) is connected to the hydraulic system by overflow oil circuit (16).
19. hydraulic systems according to any one in claim 15 to 18, it is characterised in that the hydraulic system is work
The luffing range of cantilever support hydraulic system of journey machinery, the hydraulic cylinder (4) is the driving cylinder of the luffing arm support of the engineering machinery.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201510473792.9A CN105035979B (en) | 2015-08-05 | 2015-08-05 | Balance valve group and hydraulic system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201510473792.9A CN105035979B (en) | 2015-08-05 | 2015-08-05 | Balance valve group and hydraulic system |
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| CN105035979A CN105035979A (en) | 2015-11-11 |
| CN105035979B true CN105035979B (en) | 2017-05-03 |
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| CN203175567U (en) * | 2013-01-06 | 2013-09-04 | 浙江大学 | Energy-saving type shield segment assembling positioning electrohydraulic control system adopting load-sensitive technology |
| CN104477798B (en) * | 2014-12-10 | 2016-08-17 | 中联重科股份有限公司 | Main arm variable amplitude control system of crane and crane |
| CN104595291B (en) * | 2015-01-26 | 2016-08-24 | 中联重科股份有限公司 | Energy recovery valve bank, hydraulic system of hoisting mechanism and engineering machinery |
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2015
- 2015-08-05 CN CN201510473792.9A patent/CN105035979B/en active Active
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