CN105035979A - Balance valve group and hydraulic system - Google Patents
Balance valve group and hydraulic system Download PDFInfo
- Publication number
- CN105035979A CN105035979A CN201510473792.9A CN201510473792A CN105035979A CN 105035979 A CN105035979 A CN 105035979A CN 201510473792 A CN201510473792 A CN 201510473792A CN 105035979 A CN105035979 A CN 105035979A
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- Prior art keywords
- valve
- pressure
- balance cock
- actuator port
- compensated valve
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a balance valve group and a hydraulic system. The balance valve group comprises a balance valve (100), wherein the balance valve (100) is provided with a first balance valve working port (101) leading to loads, a second balance valve work oil opening (102) leading to an oil source or an oil tank, a balance valve hydraulic control cavity (103) and a balance valve spring cavity (104), and the balance valve hydraulic control cavity (103) and the balance valve spring cavity (104) are located at the two ends of a valve element of the balance valve (100). The balance valve group further comprises a pressure compensation device connected with the balance valve (100). Therefore, when hydraulic oil sequentially passes through the first balance valve work oil opening (101) and the second balance valve work oil opening (102) from the loads and flows back to the oil tank, the pressure difference between the first balance valve work oil opening (101) and the second balance valve work oil opening (102) keeps constant, and the flow amount of the hydraulic oil passing through the balance valve (100) depends on the position of the valve element of the balance valve instead of the pressure of the loads.
Description
Technical field
The present invention relates to Hydraulic Elements, particularly, relate to a kind of balance cock group and hydraulic efficiency pressure system.
Background technology
Balance cock is the crucial Hydraulic Elements controlling the action of car hosit luffing, and it is applied in luffing mechanism hydraulic efficiency pressure system to ensure luffing mechanism smooth running.Fig. 1 shows the schematic diagram of a kind of luffing mechanism hydraulic efficiency pressure system of the prior art, comprise the hydraulic actuating cylinder 4 for supporting luffing jib connected according to diagram annexation, balance cock 100 and change-over valve 5, as can be seen from Figure 1, because the balance cock hydraulic control oil circuit 18 of balance cock 100 correspondence is identical with the rod chamber pressure of hydraulic actuating cylinder 4, so the pressure change in the rod chamber of hydraulic actuating cylinder 4 directly can affect the opening degree of balance cock 100, the impact when luffing jib declines (namely the piston rod of hydraulic actuating cylinder 4 is retracted), along with the changes in amplitude of luffing jib, the pressure of the hydraulic oil in the rodless cavity of hydraulic actuating cylinder 4 also can constantly change, then luffing jib descending speed can constantly change, thus affect the pressure (i.e. the control presssure of balance cock 100) of the rod chamber of hydraulic actuating cylinder 4, balance cock 100 can be caused so constantly to move, aperture area constantly changes, thus the stability that luffing jib declines is affected.
Fig. 2 shows the schematic diagram of another kind of luffing mechanism hydraulic efficiency pressure system of the prior art, comprise the hydraulic actuating cylinder 4 for supporting luffing jib connected according to diagram annexation, balance cock 100 and change-over valve 5, two hydraulic control ends of change-over valve 5 are connected to the first oil circuit control 5a and the second oil circuit control 5b, and, the balance cock hydraulic control oil circuit 18 of balance cock 100 correspondence is communicated with the second oil circuit control 5b (this second oil circuit control 5b is connected to bar handle) of change-over valve 5, in this luffing mechanism hydraulic efficiency pressure system, pressure size due to balance cock hydraulic control oil circuit 18 can be undertaken by the angle changing bar handle controlling (orifice size being equivalent to the spool of balance cock 100 can control by changing bar handle), so when luffing jib declines (namely the piston rod of hydraulic actuating cylinder 4 is retracted), the changes in amplitude of luffing jib or cause
The stressed change of hydraulic actuating cylinder 4, the pressure of the hydraulic oil in the rodless cavity of hydraulic actuating cylinder 4 is caused constantly to change, although the spool aperture of balance cock 100 is certain, but because before and after balance cock 100 restriction, pressure reduction constantly changes, luffing decline flow also constantly changes, and namely the retraction speed of hydraulic actuating cylinder 4 is uncontrolled.
Given this, be necessary to provide a kind of novel balance cock group, to overcome or to alleviate above-mentioned defect.
Summary of the invention
The object of this invention is to provide a kind of balance cock group, the load that the inlet outlet pressure differential of the balance cock in this balance cock group is connected with balance cock has nothing to do, and is steady state value.
Another object of the present invention is to provide a kind of hydraulic efficiency pressure system, and this hydraulic efficiency pressure system uses balance cock group provided by the invention.
To achieve these goals, the invention provides a kind of balance cock group, this balance cock group comprises balance cock, described balance cock has balance cock first actuator port for leading to load, for lead to oil sources or fuel tank balance cock second actuator port and lay respectively at this balance cock spool two ends balance cock liquid controling cavity and balance valve spring chamber, wherein, described balance cock group also comprises the pressure compensation device be connected with described balance cock, with hydraulic oil from described load successively by described balance cock first actuator port and described balance cock second actuator port and then when flowing back to fuel tank, the pressure reduction between described balance cock first actuator port and described balance cock second actuator port is made to keep constant, have nothing to do with the pressure of described load to make only to depend on the position of described balance cock spool by the flow of the hydraulic oil of described balance cock.
Preferably, described pressure compensation device comprises: priority valve, described priority valve has priority valve oil inlet, priority valve oil outlet and lay respectively at the priority valve liquid controling cavity at spool two ends of this priority valve and priority valve spring cavity and control described priority valve oil inlet and the conducting of priority valve oil outlet or cut-off can be coordinated by described priority valve liquid controling cavity and priority valve spring cavity, pressure-compensated valve, described pressure-compensated valve has pressure-compensated valve first actuator port, pressure-compensated valve second actuator port and lay respectively at the pressure-compensated valve liquid controling cavity at spool two ends of this pressure-compensated valve and pressure-compensated valve spring cavity controls the transposition of described pressure-compensated valve can be coordinated by described pressure-compensated valve liquid controling cavity and pressure-compensated valve spring cavity, wherein, described balance cock first actuator port is communicated with described priority valve liquid controling cavity, described balance cock second actuator port is communicated with described pressure-compensated valve liquid controling cavity, and described balance cock second actuator port is via the first damping unit and described priority valve oil inlet, priority valve spring cavity is communicated with pressure-compensated valve spring cavity.
Preferably, described balance cock first actuator port and described pressure-compensated valve second actuator port one-way conduction, and the direction of described one-way conduction allows the hydraulic oil of described pressure-compensated valve second actuator port to flow to described balance cock first actuator port.
Preferably, the second damping unit is provided with in described balance cock liquid controling cavity with can the application force of buffer fluid force feed to the spool of described balance cock in the process entering described balance cock liquid controling cavity.
Preferably, described balance cock is bi-bit bi-pass balance cock, and can switch between throttle position and nonreturn flow position, in described throttle position, described balance cock first actuator port is communicated with by throttling oil circuit with described balance cock second actuator port, in described nonreturn flow position, hydraulic oil can flow to described balance cock first actuator port from described balance cock second actuator port.
Preferably, described pressure-compensated valve is bi-bit bi-pass pressure-compensated valve, and can switch between throttle position and rest position, in described throttle position, described pressure-compensated valve first actuator port is communicated with by throttling oil circuit with described pressure-compensated valve second actuator port, in described rest position, described pressure-compensated valve first actuator port and described pressure-compensated valve second actuator port end each other.
Preferably, described pressure-compensated valve is 3-position-3-way pressure-compensated valve, described pressure-compensated valve also has pressure-compensated valve the 3rd actuator port, this 3-position-3-way pressure-compensated valve can be in primary importance under the effect of hydraulic oil in described pressure-compensated valve liquid controling cavity, the second place is under hydraulic oil in described pressure-compensated valve spring cavity and the effect of spring force, and the midway location that can be between described primary importance and the described second place, in described primary importance, described pressure-compensated valve first actuator port is communicated with described pressure-compensated valve the 3rd actuator port with described pressure-compensated valve second actuator port respectively, at described midway location, described pressure-compensated valve first actuator port is communicated with described pressure-compensated valve the 3rd actuator port and ends with described pressure-compensated valve second actuator port, in the described second place, described pressure-compensated valve first actuator port ends with described pressure-compensated valve second actuator port and described pressure-compensated valve the 3rd actuator port respectively.
Preferably, described balance cock group is integral type balance cock group, this integral type balance cock group comprises valve body, described valve inner comprise the spool of the described balance cock of the accommodation be communicated with successively balance cock chamber, hold the pressure compensation valve chamber of the spool of described pressure-compensated valve and hold the priority valve chamber of spool of described priority valve.
Preferably, described balance cock chamber comprises spaced described balance cock liquid controling cavity successively, balance cock first chamber and balance cock second chamber, the end being arranged in described balance cock liquid controling cavity of the spool of described balance cock is connected with piston, described piston and the perisporium of described balance cock liquid controling cavity seal and contact that described balance cock liquid controling cavity is separated into exocoel a and inner chamber b, described exocoel a is for receiving the outside hydraulic control oil circuit of described balance cock, described piston is provided with the damping plug that described exocoel a is communicated with inner chamber b, the part being arranged in described inner chamber b of the spool of described balance cock is provided with balance cock spool oil leak hole, described balance cock spool oil leak hole is communicated with described balance cock spring cavity by the passage be formed in the spool of described balance cock.
Preferably, described balance cock second chamber is communicated with described balance cock first actuator port, described balance cock first chamber is communicated with described balance cock second actuator port, the spool of described balance cock is provided with boss portion, described boss portion optionally can seal with the chamber wall between described balance cock first chamber and described balance cock second chamber when the spool of described balance cock moves and contact or interval, communicates with each other or completely cut off to make described balance cock first chamber and described balance cock second chamber.
Preferably, described balance cock first chamber is by described balance cock second actuator port and described pressure-compensated valve chamber, the spool of described pressure-compensated valve have away form one another and by pressure-compensated valve inner passage through first end and the second end, described first end is towards described balance cock second actuator port, and described second end and described valve body surround described pressure-compensated valve spring cavity.
Preferably, the spool of described pressure-compensated valve has pressure-compensated valve first cinclides be communicated with described pressure-compensated valve inner passage, described pressure-compensated valve first cinclides can optionally be communicated with described pressure-compensated valve second actuator port be formed on described valve body or end in the moving process of the spool of described pressure-compensated valve, and described pressure-compensated valve first cinclides can optionally be communicated with the middle transition chamber be formed in described valve body or end in the moving process of the spool of described pressure-compensated valve, described middle transition chamber is connected with the middle transition oil duct being provided with check valve, and described check valve allows hydraulic oil to flow to described middle transition oil duct from described middle transition chamber, described middle transition oil duct is communicated with described balance cock second chamber.
Preferably, described valve body is also formed with pressure-compensated valve the 3rd actuator port, the spool of described pressure-compensated valve has pressure-compensated valve second cinclides be communicated with described pressure-compensated valve inner passage, described pressure-compensated valve second cinclides can optionally be communicated with described pressure-compensated valve the 3rd actuator port or end in the moving process of the spool of described pressure-compensated valve.
Preferably, spaced described priority valve spring cavity is successively formed in described valve body, priority valve first chamber, priority valve second chamber and described priority valve liquid controling cavity, described pressure-compensated valve spring cavity is communicated with described priority valve second chamber by described priority valve oil inlet, the spool of described priority valve is formed with the first opening being arranged in described priority valve first chamber and the second opening being arranged in described priority valve second chamber, described first opening is by priority valve inner passage and described second open communication, described priority valve inner passage is also communicated with described priority valve spring cavity, described priority valve liquid controling cavity is communicated with described middle transition oil duct by valve inner first passage, described priority valve first chamber is communicated with valve inner second channel by described priority valve oil outlet, described valve inner second channel is communicated with described balance cock liquid controling cavity.
In addition, the present invention also provides a kind of hydraulic efficiency pressure system, wherein, this hydraulic efficiency pressure system comprises the balance cock group described in technique scheme, hydraulic actuating cylinder and change-over valve, the rod chamber of described hydraulic actuating cylinder is connected to the first actuator port of described change-over valve by the first working oil path, rodless cavity is connected to described balance cock first actuator port, described pressure-compensated valve second actuator port is connected to the second actuator port of described change-over valve by the second working oil path, the oil inlet of described change-over valve is connected with main oil-feed oil circuit and main oil return circuit respectively with return opening, and described change-over valve at least can switch to and makes described first actuator port be communicated with described oil inlet and described second actuator port is communicated with described return opening, or described first actuator port is communicated with and described second actuator port is communicated with described oil inlet with described return opening.
Preferably, two hydraulic control ends of described change-over valve are connected with the first hydraulic control oil circuit a and the second hydraulic control oil circuit b that are connected to hydraulic control handle respectively, described balance cock liquid controling cavity is connected with described second hydraulic control oil circuit b by balance cock hydraulic control oil circuit, and the hydraulic oil in described second hydraulic control oil circuit b can control described change-over valve and commutate to the working position of the piston rod retraction movement making described hydraulic actuating cylinder.
Preferably, described pressure-compensated valve also has pressure-compensated valve the 3rd actuator port, and described pressure-compensated valve at least can switch to and makes described pressure-compensated valve first actuator port be communicated with described pressure-compensated valve the 3rd actuator port, described pressure-compensated valve the 3rd actuator port is connected to energy-storage module.
Preferably, described pressure-compensated valve is 3-position-3-way pressure-compensated valve, this 3-position-3-way pressure-compensated valve can be in primary importance under the effect of hydraulic oil in described pressure-compensated valve liquid controling cavity, the second place is under the effect of the hydraulic oil in described pressure-compensated valve spring cavity, and the control position that can be between described primary importance and the described second place, in described primary importance, described pressure-compensated valve first actuator port is communicated with described pressure-compensated valve the 3rd actuator port with described pressure-compensated valve second actuator port respectively, at described midway location, described pressure-compensated valve first actuator port is communicated with described pressure-compensated valve the 3rd actuator port and ends with described pressure-compensated valve second actuator port, in the described second place, described pressure-compensated valve first actuator port ends with described pressure-compensated valve second actuator port and described pressure-compensated valve the 3rd actuator port respectively.
Preferably, described energy-storage module comprises energy storage, and described energy storage is connected to the fuel tank of described hydraulic efficiency pressure system by overflow oil circuit.
Preferably, described hydraulic efficiency pressure system is the luffing range of cantilever support hydraulic efficiency pressure system of construction machinery and equipment, and described hydraulic actuating cylinder is the driving cylinder of the luffing jib of described construction machinery and equipment.
Pass through technique scheme, because described balance cock group also comprises the pressure compensation device be connected with described balance cock, with hydraulic oil from described load successively by described balance cock first actuator port and described balance cock second actuator port and then when flowing back to fuel tank, the pressure reduction between described balance cock first actuator port and described balance cock second actuator port is made to keep constant, have nothing to do with the pressure of described load to make only to depend on the position of described balance cock spool by the flow of the hydraulic oil of described balance cock, so the import and export of balance cock in this balance cock group (when hydraulic oil by load flow to balance cock time, import and export are respectively balance cock first actuator port and balance cock second actuator port) load that is connected with balance cock of pressure reduction has nothing to do, for steady state value, especially, when this balance cock group is applied in the luffing range of cantilever support hydraulic efficiency pressure system of construction machinery and equipment (such as hoisting crane), jib descending speed can be controlled by the valve core opening area of the device manipulation balance cocks such as operating handle, thus jib is steadily declined, this is because jib descending speed depends on the flow of the hydraulic oil flowing through balance cock, and the hydraulic fluid flow rate flowing through balance cock is relevant with balance cock inlet outlet pressure differential with the valve core opening area of balance cock, if guarantee balance cock inlet outlet pressure differential is constant and the valve core opening constant area of balance cock, can ensure by the hydraulic fluid flow rate of balance cock certain.
Other features and advantages of the present invention are 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 forms a part for specification sheets, is used from explanation the present invention, but is not construed as limiting the invention with detailed description of the invention one below.In the accompanying drawings:
Fig. 1 is the schematic diagram of a kind of luffing mechanism hydraulic efficiency pressure system of the prior art.
Fig. 2 is the schematic diagram of another kind of luffing mechanism hydraulic efficiency pressure system of the prior art.
Fig. 3 is the schematic diagram of balance cock group according to the embodiment of the present invention.
Fig. 4 is the cutaway view of the balance cock group according to a kind of detailed description of the invention of the present invention.
Fig. 5 is the cutaway view of the balance cock group according to another kind of detailed description of the invention of the present invention.
Fig. 6 is the schematic diagram of the hydraulic efficiency pressure system according to a kind of detailed description of the invention of the present invention.
Fig. 7 is the schematic diagram of the hydraulic efficiency pressure system according to another kind of detailed description of the invention of the present invention.
Description of reference numerals
1 first damping unit 2 second damping unit
3 check valve 4 hydraulic actuating cylinders
5 change-over valve 6 first working oil path
The middle oil circuit of 7 second working oil path 8 first
The middle oil circuit of 9 draining oil circuit 10 second
11 the 3rd middle oil circuit 12 Hydraulic Pumps
The main oil return circuit of 13 main oil-feed oil circuit 14
15 energy storage 16 overflow oil circuits
17 by pass valve 18 balance cock hydraulic control oil circuits
5a first oil circuit control 5b second oil circuit control
51 first actuator port 52 second actuator ports
100 balance cock 101 balance cock first actuator ports
102 balance cock second actuator port 103 balance cock liquid controling cavities
103a exocoel 103b inner chamber
104 balance cock spring cavity 105 balance cock first chambeies
106 balance cock second chamber 107 pistons
108 balance cock spool oil leak hole 109 boss portion
110 drain tap 200 priority valves
201 priority valve oil inlet 202 priority valve oil outlets
203 priority valve liquid controling cavity 204 priority valve spring cavitys
205 priority valve second chamber, priority valve first chambeies 206
207 first opening 208 second openings
300 pressure-compensated valve 301 pressure-compensated valve first actuator ports
302 pressure-compensated valve second actuator port 303 pressure-compensated valve liquid controling cavities
304 pressure-compensated valve spring cavity 305 pressure-compensated valve the 3rd actuator ports
306 pressure compensation valve spring 307 pressure-compensated valve first cinclides
308 pressure-compensated valve second cinclides 400 valve bodies
401 middle transition chamber 402 middle transition oil ducts
403 valve inner first passage 404 valve inner second channels
The external passage of 405 external hydraulic fluid port 406
407 valve pocket 408 valve pocket holes
Detailed description of the invention
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described in detail.Should be understood that, detailed description of the invention described herein, only for instruction and explanation of the present invention, is not limited to the present invention.
See Fig. 3, according to an aspect of the present invention, provide a kind of balance cock group, this balance cock group comprises balance cock 100, balance cock 100 has balance cock first actuator port 101 for leading to load, for leading to balance cock second actuator port 102 of oil sources or fuel tank and laying respectively at the balance cock liquid controling cavity 103 at spool two ends of this balance cock 100 and balance valve spring chamber 104 and control balance cock 100 replace can be coordinated by balance cock liquid controling cavity 103 and balance valve spring chamber 104, wherein, balance cock group also comprises the pressure compensation device be connected with balance cock 100, with hydraulic oil from load successively by balance cock first actuator port 101 and balance cock second actuator port 102 and then when flowing back to fuel tank, the pressure reduction between balance cock first actuator port 101 and balance cock second actuator port 102 is made to keep constant, have nothing to do with the pressure of load to make only to depend on the position of balance cock spool by the flow of the hydraulic oil of balance cock 100.
As mentioned above, because balance cock group also comprises the pressure compensation device be connected with balance cock 100, with hydraulic oil from load successively by balance cock first actuator port 101 and balance cock second actuator port 102 and then when flowing back to fuel tank, the pressure reduction between balance cock first actuator port 101 and balance cock second actuator port 102 is made to keep constant, have nothing to do with the pressure of load to make only to depend on the position of balance cock spool by the flow of the hydraulic oil of balance cock 100, so the import and export of balance cock 100 in this balance cock group (when hydraulic oil by load flow to balance cock 100 time, import and export are respectively balance cock first actuator port 101 and balance cock second actuator port 102) load that is connected with balance cock 100 of pressure reduction has nothing to do, for steady state value, especially, when this balance cock group is applied in the luffing range of cantilever support hydraulic efficiency pressure system of construction machinery and equipment (such as hoisting crane), jib descending speed can be controlled by the valve core opening area of the device manipulation balance cocks 100 such as operating handle, thus jib is steadily declined, this is because jib descending speed depends on the flow of the hydraulic oil flowing through balance cock 100, and the hydraulic fluid flow rate flowing through balance cock 100 is relevant with balance cock inlet outlet pressure differential with the valve core opening area of balance cock 100, if guarantee balance cock inlet outlet pressure differential is constant and the valve core opening constant area of balance cock, can ensure by the hydraulic fluid flow rate of balance cock 100 certain.
According to the preferred embodiment of the present invention, pressure compensation device can comprise: priority valve 200, priority valve 200 has priority valve oil inlet 201, priority valve oil outlet 202 and lay respectively at the priority valve liquid controling cavity 203 at spool two ends of this priority valve 200 and priority valve spring cavity 204 controls priority valve oil inlet 201 and priority valve oil outlet 202 conducting or cut-off can be coordinated by priority valve liquid controling cavity 203 and priority valve spring cavity 204, pressure-compensated valve 300, pressure-compensated valve 300 has pressure-compensated valve first actuator port 301, pressure-compensated valve second actuator port 302 and lay respectively at the pressure-compensated valve liquid controling cavity 303 at spool two ends of this pressure-compensated valve 300 and pressure-compensated valve spring cavity 304 control presssure throttle compensating valve 300 being coordinated to replace by pressure-compensated valve liquid controling cavity 303 and pressure-compensated valve spring cavity 304, wherein, balance cock first actuator port 101 is communicated with priority valve liquid controling cavity 203, balance cock second actuator port 102 is communicated with pressure-compensated valve liquid controling cavity 303, and balance cock second actuator port 102 is via the first damping unit 1 and priority valve oil inlet 201, priority valve spring cavity 204 is communicated with pressure-compensated valve spring cavity 304.
The balance cock group made a concrete analysis of below in above-mentioned preferred implementation how to ensure that between balance cock first actuator port 101 of balance cock 100 and balance cock second actuator port 102, pressure reduction is constant:
Suppose that balance cock first actuator port 101 is communicated with priority valve liquid controling cavity 203 by the first middle oil circuit 8, balance cock second actuator port 102 is communicated with pressure-compensated valve liquid controling cavity 303 by the second middle oil circuit 10, balance cock second actuator port 102 is via after the first damping unit 1, be communicated with pressure-compensated valve spring cavity 304 with priority valve oil inlet 201 via after the 3rd middle oil circuit 11 again, composition graphs 3 is analyzed, hydraulic fluid pressure when balance cock first actuator port 101 place is Pb, the hydraulic fluid pressure at balance cock second actuator port 102 place is Pa, hydraulic fluid pressure on 3rd middle oil circuit 11 is Pc, the spring force of pressure-compensated valve spring cavity 304 is f1, when the spring force of priority valve spring cavity 204 is f2, can be easy to draw the hydraulic fluid pressure=Pb on the middle oil circuit 8 of hydraulic fluid pressure=the first in priority valve liquid controling cavity 203 according to the hydraulic connecting relation in figure, hydraulic fluid pressure=Pa on the middle oil circuit 10 of hydraulic fluid pressure=the second of pressure-compensated valve liquid controling cavity 303, and the hydraulic fluid pressure in priority valve spring cavity 204 and pressure-compensated valve spring cavity 304 equals the hydraulic fluid pressure Pc on the 3rd middle oil circuit 11 respectively, when priority valve 200 and pressure-compensated valve 300 reach dynamical equilibrium respectively, there is Pb=Pc+f2, Pa=Pc+f1, thus Pb-Pa=f2-f1, that is, pressure reduction between balance cock first actuator port 101 and balance cock second actuator port 102 is determined by the difference of the spring force in the spring force in priority valve 200 and pressure-compensated valve 300, as long as have selected priority valve 200 and pressure-compensated valve 300, this difference is steady state value.
In addition, balance cock first actuator port 101 can with pressure-compensated valve second actuator port 302 one-way conduction, and the hydraulic oil of direction authorized pressure throttle compensating valve second actuator port 302 of one-way conduction flows to balance cock first actuator port 101, particularly, balance cock first actuator port 101 can by being provided with oil circuit and pressure-compensated valve second actuator port 302 one-way conduction of check valve 3, the unnecessary running of hydraulic power oil of a part at pressure-compensated valve second actuator port 302 place can be made like this to balance cock first actuator port 101, when this balance cock group is applied in the luffing range of cantilever support hydraulic efficiency pressure system of construction machinery and equipment (such as hoisting crane), balance cock first actuator port 101 can be connected to the rodless cavity of the driving cylinder of jib, so the unnecessary running of hydraulic power oil of a part at pressure-compensated valve second actuator port 302 place to balance cock first actuator port 101 may be used for hoisting (piston rod corresponding to driving cylinder stretches out) fuel feeding to jib.
Preferably, be provided with in balance cock liquid controling cavity 103 second damping unit 2 (can be damping plug etc.) with can buffer fluid force feed in the process entering balance cock liquid controling cavity 103 to the application force of the spool of balance cock 100.
In addition, balance cock spring cavity 104, priority valve oil outlet 202 can also be connected to draining oil circuit 9, this draining oil circuit 9 for connecting fuel tank the unnecessary hydraulic oil of balance cock spring cavity 104 and priority valve oil outlet 202 is discharged.
As can be seen from Figure 3, balance cock 100 is preferably bi-bit bi-pass balance cock, and can switch between throttle position and nonreturn flow position, in throttle position, balance cock first actuator port 101 is communicated with by throttling oil circuit with balance cock second actuator port 102, in nonreturn flow position, hydraulic oil can flow to balance cock first actuator port 101 from balance cock second actuator port 102, but balance cock 100 is obviously not limited to bi-bit bi-pass balance cock.
In addition, pressure-compensated valve 300 is preferably bi-bit bi-pass pressure-compensated valve, and can switch between throttle position and rest position, in throttle position, pressure-compensated valve first actuator port 301 is communicated with by throttling oil circuit with pressure-compensated valve second actuator port 302, in rest position, pressure-compensated valve first actuator port 301 and pressure-compensated valve second actuator port 302 end each other, but pressure-compensated valve 300 is obviously not limited to bi-bit bi-pass pressure-compensated valve, such as, , pressure-compensated valve 300 can also be 3-position-3-way pressure-compensated valve, pressure-compensated valve 300 can also have pressure-compensated valve the 3rd actuator port 305, this 3-position-3-way pressure-compensated valve can be in primary importance under the effect of hydraulic oil in pressure-compensated valve liquid controling cavity 303, the second place is under hydraulic oil in pressure-compensated valve spring cavity 304 and the effect of spring force, and the midway location that can be between primary importance and the second place, in primary importance, pressure-compensated valve first actuator port 301 is communicated with pressure-compensated valve the 3rd actuator port 305 with pressure-compensated valve second actuator port 302 respectively, at midway location, pressure-compensated valve first actuator port 301 is communicated with pressure-compensated valve the 3rd actuator port 305 and ends with pressure-compensated valve second actuator port 302, in the second place, pressure-compensated valve first actuator port 301 ends with pressure-compensated valve second actuator port 302 and pressure-compensated valve the 3rd actuator port 305 respectively.
See Fig. 4 and Fig. 5, balance cock group can be integral type balance cock group, this integral type balance cock group can comprise valve body 400, and valve body 400 inside comprises the priority valve chamber of the spool of the balance cock chamber of the spool of the accommodation balance cock 100 be communicated with successively, the pressure compensation valve chamber holding the spool of pressure-compensated valve 300 and accommodation priority valve 200.
See Fig. 4, according to a kind of detailed description of the invention of the present invention, balance cock chamber can comprise spaced balance cock liquid controling cavity 103 successively, balance cock first chamber 105 and balance cock second chamber 106, the end being arranged in balance cock liquid controling cavity 103 of the spool of balance cock 100 is connected with piston 107, piston 107 and the perisporium of balance cock liquid controling cavity 103 seal and contact that balance cock liquid controling cavity 103 is separated into exocoel 103a and inner chamber 103b, exocoel 103a is used for the outside hydraulic control oil circuit of receiving balance valve 100, such as be connected to balance cock hydraulic control oil circuit 18 by the external passage 406 on a valve gap, piston 107 is provided with the damping plug (i.e. the second damping unit 2 above-mentioned) that exocoel 103a is communicated with inner chamber 103b, the part being arranged in inner chamber 103b of the spool of balance cock 100 is provided with balance cock spool oil leak hole 108, balance cock spool oil leak hole 108 is communicated with balance cock spring cavity 104 by the passage be formed in the spool of balance cock 100, balance cock spring cavity 104 can be connected with the external hydraulic fluid port 405 on another valve gap, this external hydraulic fluid port 405 is for being connected for draining with fuel tank.
In addition, balance cock second chamber 106 is communicated with balance cock first actuator port 101, balance cock first chamber 105 is communicated with balance cock second actuator port 102, the spool of balance cock 100 is provided with boss portion 109, boss portion 109 optionally can seal with the chamber wall between balance cock first chamber 105 and balance cock second chamber 106 when the spool of balance cock 100 moves and contact or interval, communicates with each other or completely cut off to make balance cock first chamber 105 and balance cock second chamber 106.Balance cock first chamber 105 can by balance cock second actuator port 102 and pressure-compensated valve chamber, the spool of pressure-compensated valve 300 have away form one another and by pressure-compensated valve inner passage through first end and the second end, first end surrounds pressure-compensated valve spring cavity 304 towards balance cock second actuator port 102, second end and valve body 400.
In addition, the spool of pressure-compensated valve 300 has pressure-compensated valve first cinclides 307 be communicated with pressure-compensated valve inner passage, pressure-compensated valve first cinclides 307 can be optionally communicated with by the valve pocket hole 408 on valve pocket 407 with pressure-compensated valve second actuator port 302 be formed on valve body 400 or end in the moving process of the spool of pressure-compensated valve 300, and pressure-compensated valve first cinclides 307 can be optionally communicated with by the valve pocket hole 408 on valve pocket 407 with the middle transition chamber 401 be formed in valve body 400 or end in the moving process of the spool of pressure-compensated valve 300, middle transition chamber 401 is connected with the middle transition oil duct 402 being provided with check valve 3, and check valve 3 allows hydraulic oil to flow to middle transition oil duct 402 from middle adapter cavity 401, middle transition oil duct 402 is communicated with balance cock second chamber 106.
Preferably, see Fig. 5, valve body 400 also can be formed with pressure-compensated valve the 3rd actuator port 305, the spool of pressure-compensated valve 300 has pressure-compensated valve second cinclides 308 be communicated with pressure-compensated valve inner passage, pressure-compensated valve second cinclides 308 can optionally be communicated with pressure-compensated valve the 3rd actuator port 305 or end in the moving process of the spool of pressure-compensated valve 300.
In addition, spaced priority valve spring cavity 204 successively can be formed with in valve body 400, priority valve first chamber 205, priority valve second chamber 206 and priority valve liquid controling cavity 203, pressure-compensated valve spring cavity 304 can be communicated with priority valve second chamber 206 by priority valve oil inlet 201, the spool of priority valve 200 can be formed with the first opening 207 being arranged in priority valve first chamber 205 and the second opening 208 being arranged in priority valve second chamber 206, first opening 207 is communicated with the second opening 208 by priority valve inner passage, priority valve inner passage is also communicated with priority valve spring cavity 204, priority valve liquid controling cavity 203 is communicated with middle transition oil duct 402 by valve inner first passage 403, priority valve first chamber 205 is communicated with valve inner second channel 404 by priority valve oil outlet 202, valve inner second channel 404 is communicated with balance cock liquid controling cavity 103.
As can be seen from Figure 5, according to another kind of detailed description of the invention of the present invention, valve body 400 can be formed with the drain tap 110 be communicated with balance cock liquid controling cavity 103, drain tap 110 is for connecting fuel tank, thus the unnecessary hydraulic oil that can be released by drain tap 110 in balance cock liquid controling cavity 103, and, when priority valve 200 is opened, hydraulic oil in priority valve 200 also can arrive balance cock liquid controling cavity 103 by way of valve inner second channel 404, and then flows back into fuel tank by drain tap 110.
See Fig. 6 and Fig. 7, according to another aspect of the present invention, a kind of hydraulic efficiency pressure system is provided, wherein, this hydraulic efficiency pressure system comprises above-mentioned balance cock group, hydraulic actuating cylinder 4 and change-over valve 5, the rod chamber of hydraulic actuating cylinder 4 is connected to the first actuator port 51 of change-over valve 5 by the first working oil path 6, rodless cavity is connected to balance cock first actuator port 101, pressure-compensated valve second actuator port 302 is connected to the second actuator port 52 of change-over valve 5 by the second working oil path 7, the oil inlet 53 of change-over valve 5 is connected with main oil-feed oil circuit 13 and main oil return circuit 14 respectively with return opening 54, and change-over valve 5 at least can switch to and makes the first actuator port 51 be communicated with oil inlet and the second actuator port 52 is communicated with return opening, or the first actuator port 51 is communicated with and the second actuator port 52 is communicated with oil inlet with return opening.Because this hydraulic efficiency pressure system comprises above-mentioned balance cock, so known based on the advantage of above-mentioned balance cock, will be more steady when the piston rod of hydraulic actuating cylinder 4 is retracted, and speed is controlled.
Particularly, two hydraulic control ends of change-over valve 5 can be connected with the first hydraulic control oil circuit 5a and the second hydraulic control oil circuit 5b that are connected to hydraulic control handle respectively, balance cock liquid controling cavity 103 is connected with the second hydraulic control oil circuit 5b by balance cock hydraulic control oil circuit 18, hydraulic oil in second hydraulic control oil circuit 5b can control change-over valve 5 and commutate to the working position of the piston rod retraction movement making hydraulic actuating cylinder 4, so can be carried out the retraction speed of the piston rod of hydraulic control cylinder 4 by operation hydraulic control handle.
Above-mentioned hydraulic efficiency pressure system is preferably the luffing range of cantilever support hydraulic efficiency pressure system for construction machinery and equipment, hydraulic actuating cylinder 4 can be the driving cylinder of the luffing jib of construction machinery and equipment (such as hoisting crane), owing to refer to when this balance cock group is applied in the luffing range of cantilever support hydraulic efficiency pressure system of construction machinery and equipment above, jib descending speed can be controlled by the valve core opening area of the device manipulation balance cocks 100 such as operating handle, thus jib is steadily declined.Here no longer repeat specification is carried out to these advantages.
In addition, pressure-compensated valve the 3rd actuator port 305 can be connected to energy-storage module, thus when pressure-compensated valve first actuator port 301 is communicated with pressure-compensated valve the 3rd actuator port 305, a part of hydraulic oil in the rodless cavity of hydraulic actuating cylinder 4 is stored to energy-storage module.
The particular type of energy-storage module is also not particularly limited, and such as, energy-storage module can comprise energy storage 15, and energy storage 15 can be connected to the fuel tank of hydraulic efficiency pressure system by the overflow oil circuit 16 being provided with by pass valve 17.
Below the preferred embodiment of the present invention is described in detail by reference to the accompanying drawings; but; the present invention is not limited to the detail in above-mentioned embodiment; within the scope of technical conceive of the present invention; can carry out multiple simple variant to technical scheme of the present invention, these simple variant all belong to protection scope of the present invention.
It should be noted that in addition, each the concrete technical characteristic described in above-mentioned detailed description of the invention, in reconcilable situation, can be combined by any suitable mode.In order to avoid unnecessary repetition, the present invention illustrates no longer separately to various possible array mode.
In addition, also can carry out combination in any between various different embodiment of the present invention, as long as it is without prejudice to thought of the present invention, it should be considered as content disclosed in this invention equally.
Claims (20)
1. balance cock group, this balance cock group comprises balance cock (100), described balance cock (100) has balance cock first actuator port (101) for leading to load, for leading to balance cock second actuator port (102) of oil sources or fuel tank and laying respectively at the balance cock liquid controling cavity (103) at spool two ends and balance valve spring chamber (104) of this balance cock (100), it is characterized in that
Described balance cock group also comprises the pressure compensation device be connected with described balance cock (100), with hydraulic oil from described load successively by described balance cock first actuator port (101) and described balance cock second actuator port (102) and then when flowing back to fuel tank, make the pressure reduction between described balance cock first actuator port (101) and described balance cock second actuator port (102) keep constant, have nothing to do with the pressure of described load to make only to depend on the position of described balance cock spool by the flow of the hydraulic oil of described balance cock (100).
2. balance cock group according to claim 1, is characterized in that, described pressure compensation device comprises:
Priority valve (200), described priority valve (200) has priority valve oil inlet (201), priority valve oil outlet (202) and lays respectively at the priority valve liquid controling cavity (203) at spool two ends of this priority valve (200) and priority valve spring cavity (204) controls described priority valve oil inlet (201) and (202) conducting of priority valve oil outlet or cut-off can be coordinated by described priority valve liquid controling cavity (203) and priority valve spring cavity (204)
Pressure-compensated valve (300), described pressure-compensated valve (300) is had pressure-compensated valve first actuator port (301), pressure-compensated valve second actuator port (302) and lays respectively at the pressure-compensated valve liquid controling cavity (303) at spool two ends of this pressure-compensated valve (300) and pressure-compensated valve spring cavity (304) and controls described pressure-compensated valve (300) replace can be coordinated by described pressure-compensated valve liquid controling cavity (303) and pressure-compensated valve spring cavity (304)
Wherein, described balance cock first actuator port (101) is communicated with described priority valve liquid controling cavity (203), described balance cock second actuator port (102) is communicated with described pressure-compensated valve liquid controling cavity (303), and described balance cock second actuator port (102) is communicated with pressure-compensated valve spring cavity (304) with described priority valve oil inlet (201), priority valve spring cavity (204) via the first damping unit (1).
3. balance cock group according to claim 2, it is characterized in that, described balance cock first actuator port (101) and described pressure-compensated valve second actuator port (302) one-way conduction, and the direction of described one-way conduction allows the hydraulic oil of described pressure-compensated valve second actuator port (302) to flow to described balance cock first actuator port (101).
4. balance cock group according to claim 1, it is characterized in that, be provided with the second damping unit (2) in described balance cock liquid controling cavity (103) with can the application force of buffer fluid force feed to the spool of described balance cock (100) in the process entering described balance cock liquid controling cavity (103).
5. balance cock group as claimed in any of claims 1 to 4, it is characterized in that, described balance cock (100) is bi-bit bi-pass balance cock, and can switch between throttle position and nonreturn flow position, in described throttle position, described balance cock first actuator port (101) is communicated with by throttling oil circuit with described balance cock second actuator port (102), in described nonreturn flow position, hydraulic oil can flow to described balance cock first actuator port (101) from described balance cock second actuator port (102).
6. balance cock group as claimed in any of claims 2 to 4, it is characterized in that, described pressure-compensated valve (300) is bi-bit bi-pass pressure-compensated valve, and can switch between throttle position and rest position, in described throttle position, described pressure-compensated valve first actuator port (301) is communicated with by throttling oil circuit with described pressure-compensated valve second actuator port (302), in described rest position, described pressure-compensated valve first actuator port (301) and described pressure-compensated valve second actuator port (302) are ended each other.
7. balance cock group as claimed in any of claims 2 to 4, it is characterized in that, described pressure-compensated valve (300) is 3-position-3-way pressure-compensated valve, described pressure-compensated valve (300) also has pressure-compensated valve the 3rd actuator port (305), this 3-position-3-way pressure-compensated valve can be in primary importance under the effect of hydraulic oil in described pressure-compensated valve liquid controling cavity (303), the second place is under hydraulic oil in described pressure-compensated valve spring cavity (304) and the effect of spring force, and the midway location that can be between described primary importance and the described second place, in described primary importance, described pressure-compensated valve first actuator port (301) is communicated with described pressure-compensated valve the 3rd actuator port (305) with described pressure-compensated valve second actuator port (302) respectively, at described midway location, described pressure-compensated valve first actuator port (301) is communicated with described pressure-compensated valve the 3rd actuator port (305) and ends with described pressure-compensated valve second actuator port (302), in the described second place, described pressure-compensated valve first actuator port (301) is ended with described pressure-compensated valve second actuator port (302) and described pressure-compensated valve the 3rd actuator port (305) respectively.
8. balance cock group as claimed in any of claims 2 to 4, it is characterized in that, described balance cock group is integral type balance cock group, this integral type balance cock group comprises valve body (400), and described valve body (400) inside comprises the balance cock chamber of the spool of the described balance cock of the accommodation be communicated with successively (100), holds the priority valve chamber of the pressure compensation valve chamber of the spool of described pressure-compensated valve (300) and the spool of the described priority valve of accommodation (200).
9. balance cock group according to claim 8, it is characterized in that, described balance cock chamber comprises spaced described balance cock liquid controling cavity (103) successively, balance cock first chamber (105) and balance cock second chamber (106), the end being arranged in described balance cock liquid controling cavity (103) of the spool of described balance cock (100) is connected with piston (107), described piston (107) and the perisporium of described balance cock liquid controling cavity (103) seal and contact that described balance cock liquid controling cavity (103) is separated into exocoel (103a) and inner chamber (103b), described exocoel (103a) is for receiving the outside hydraulic control oil circuit of described balance cock (100), described piston (107) is provided with the damping plug that described exocoel (103a) is communicated with inner chamber (103b), the part being arranged in described inner chamber (103b) of the spool of described balance cock (100) is provided with balance cock spool oil leak hole (108), described balance cock spool oil leak hole (108) is communicated with described balance cock spring cavity (104) by the interior passage being formed in the spool of described balance cock (100).
10. balance cock group according to claim 9, it is characterized in that, described balance cock second chamber (106) is communicated with described balance cock first actuator port (101), described balance cock first chamber (105) is communicated with described balance cock second actuator port (102), the spool of described balance cock (100) is provided with boss portion (109), described boss portion (109) optionally can seal with the chamber wall between described balance cock first chamber (105) and described balance cock second chamber (106) when the spool of described balance cock (100) moves and contact or interval, communicate with each other to make described balance cock first chamber (105) and described balance cock second chamber (106) or completely cut off.
11. balance cock groups according to claim 10, it is characterized in that, described balance cock first chamber (105) is by described balance cock second actuator port (102) and described pressure-compensated valve chamber, the spool of described pressure-compensated valve (300) have away form one another and by pressure-compensated valve inner passage through first end and the second end, described first end is towards described balance cock second actuator port (102), and described second end and described valve body (400) surround described pressure-compensated valve spring cavity (304).
12. balance cock groups according to claim 11, it is characterized in that, the spool of described pressure-compensated valve (300) has pressure-compensated valve first cinclides (307) be communicated with described pressure-compensated valve inner passage, described pressure-compensated valve first cinclides (307) can optionally be communicated with described pressure-compensated valve second actuator port (302) be formed on described valve body (400) or end in the moving process of the spool of described pressure-compensated valve (300), and described pressure-compensated valve first cinclides (307) can optionally be communicated with the middle transition chamber (401) be formed in described valve body (400) or end in the moving process of the spool of described pressure-compensated valve (300), described middle transition chamber (401) is connected with the middle transition oil duct (402) being provided with check valve (3), and described check valve (3) allows hydraulic oil to flow to described middle transition oil duct (402) from described middle transition chamber (401), described middle transition oil duct (402) is communicated with described balance cock second chamber (106).
13. balance cock groups according to claim 12, it is characterized in that, described valve body (400) is also formed with pressure-compensated valve the 3rd actuator port (305), the spool of described pressure-compensated valve (300) has pressure-compensated valve second cinclides (308) be communicated with described pressure-compensated valve inner passage, described pressure-compensated valve second cinclides (308) can optionally be communicated with described pressure-compensated valve the 3rd actuator port (305) or end in the moving process of the spool of described pressure-compensated valve (300).
14. balance cock groups according to claim 12, it is characterized in that, spaced described priority valve spring cavity (204) is successively formed in described valve body (400), priority valve first chamber (205), priority valve second chamber (206) and described priority valve liquid controling cavity (203), described pressure-compensated valve spring cavity (304) is communicated with described priority valve second chamber (206) by described priority valve oil inlet (201), the spool of described priority valve (200) is formed with the first opening (207) being arranged in described priority valve first chamber (205) and the second opening (208) being arranged in described priority valve second chamber (206), described first opening (207) is communicated with described second opening (208) by priority valve inner passage, described priority valve inner passage is also communicated with described priority valve spring cavity (204), described priority valve liquid controling cavity (203) is communicated with described middle transition oil duct (402) by valve inner first passage (403), described priority valve first chamber (205) is communicated with valve inner second channel (404) by described priority valve oil outlet (202), described valve inner second channel (404) is communicated with described balance cock liquid controling cavity (103).
15. 1 kinds of hydraulic efficiency pressure systems, it is characterized in that, this hydraulic efficiency pressure system comprises balance cock group as claimed in any of claims 2 to 4, hydraulic actuating cylinder (4) and change-over valve (5), the rod chamber of described hydraulic actuating cylinder (4) is connected to first actuator port (51) of described change-over valve (5) by the first working oil path (6), rodless cavity is connected to described balance cock first actuator port (101), described pressure-compensated valve second actuator port (302) is connected to second actuator port (52) of described change-over valve (5) by the second working oil path (7), the oil inlet of described change-over valve (5) is connected with main oil-feed oil circuit (13) and main oil return circuit (14) respectively with return opening, and described change-over valve (5) at least can switch to and makes described first actuator port (51) be communicated with described oil inlet and described second actuator port (52) is communicated with described return opening, or described first actuator port (51) is communicated with and described second actuator port (52) is communicated with described oil inlet with described return opening.
16. hydraulic efficiency pressure systems according to claim 15, it is characterized in that, two hydraulic control ends of described change-over valve (5) are connected with the first hydraulic control oil circuit (5a) and the second hydraulic control oil circuit (5b) that are connected to hydraulic control handle respectively, described balance cock liquid controling cavity (103) is connected with described second hydraulic control oil circuit (5b) by balance cock hydraulic control oil circuit (18), and the hydraulic oil in described second hydraulic control oil circuit (5b) can control described change-over valve (5) and commutate to the working position of the piston rod retraction movement making described hydraulic actuating cylinder (4).
17. hydraulic efficiency pressure systems according to claim 15, it is characterized in that, described pressure-compensated valve (300) also has pressure-compensated valve the 3rd actuator port (305), and described pressure-compensated valve (300) at least can switch to and makes described pressure-compensated valve first actuator port (301) be communicated with described pressure-compensated valve the 3rd actuator port (305), described pressure-compensated valve the 3rd actuator port (305) is connected to energy-storage module.
18. hydraulic efficiency pressure systems according to claim 17, it is characterized in that, described pressure-compensated valve (300) is 3-position-3-way pressure-compensated valve, this 3-position-3-way pressure-compensated valve can be in primary importance under the effect of hydraulic oil in described pressure-compensated valve liquid controling cavity (303), the second place is under the effect of the hydraulic oil in described pressure-compensated valve spring cavity (304), and the control position that can be between described primary importance and the described second place, in described primary importance, described pressure-compensated valve first actuator port (301) is communicated with described pressure-compensated valve the 3rd actuator port (305) with described pressure-compensated valve second actuator port (302) respectively, at described midway location, described pressure-compensated valve first actuator port (301) is communicated with described pressure-compensated valve the 3rd actuator port (305) and ends with described pressure-compensated valve second actuator port (302), in the described second place, described pressure-compensated valve first actuator port (301) is ended with described pressure-compensated valve second actuator port (302) and described pressure-compensated valve the 3rd actuator port (305) respectively.
19. hydraulic efficiency pressure systems according to claim 17, is characterized in that, described energy-storage module comprises energy storage (15), and described energy storage (15) is connected to the fuel tank of described hydraulic efficiency pressure system by overflow oil circuit (16).
20. according to claim 16 to the hydraulic efficiency pressure system described in any one in 19, and it is characterized in that, described hydraulic efficiency pressure system is the driving cylinder of the luffing range of cantilever support hydraulic efficiency pressure system of construction machinery and equipment, the luffing jib that described hydraulic actuating cylinder (4) is described construction machinery and equipment.
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| CN110939622A (en) * | 2018-09-21 | 2020-03-31 | 伊顿智能动力有限公司 | Hydraulic pressure compensator with integrated load sensing |
| CN111664136A (en) * | 2020-05-25 | 2020-09-15 | 圣邦集团有限公司 | Load compensation balance valve |
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| CN110725819A (en) * | 2019-08-26 | 2020-01-24 | 宁波江北宇洲液压设备厂 | Flow control type variable amplitude balance valve |
| CN110725819B (en) * | 2019-08-26 | 2021-07-16 | 宁波宇洲液压设备有限公司 | Flow control type variable amplitude balance valve |
| CN111664136A (en) * | 2020-05-25 | 2020-09-15 | 圣邦集团有限公司 | Load compensation balance valve |
| CN111664136B (en) * | 2020-05-25 | 2024-04-19 | 圣邦集团有限公司 | Load compensation balance valve |
| CN111795028A (en) * | 2020-07-03 | 2020-10-20 | 大连海事大学 | Pressure difference and flow composite control's water pressure artificial muscle joint control valve |
| CN111795028B (en) * | 2020-07-03 | 2022-04-08 | 大连海事大学 | Pressure difference and flow composite control's water pressure artificial muscle joint control valve |
| CN111828420A (en) * | 2020-07-08 | 2020-10-27 | 江苏汇智高端工程机械创新中心有限公司 | Hydraulic compensation balance valve |
| CN111828420B (en) * | 2020-07-08 | 2022-05-17 | 江苏汇智高端工程机械创新中心有限公司 | Hydraulic compensation balance valve |
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