CN108317117A - A kind of double nargin SERVO CONTROL valve groups of low throttling noise - Google Patents
A kind of double nargin SERVO CONTROL valve groups of low throttling noise Download PDFInfo
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- CN108317117A CN108317117A CN201810284178.1A CN201810284178A CN108317117A CN 108317117 A CN108317117 A CN 108317117A CN 201810284178 A CN201810284178 A CN 201810284178A CN 108317117 A CN108317117 A CN 108317117A
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- 238000006073 displacement reaction Methods 0.000 claims abstract description 27
- 230000005611 electricity Effects 0.000 claims description 8
- 239000002828 fuel tank Substances 0.000 claims description 3
- 230000009131 signaling function Effects 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 31
- 239000000446 fuel Substances 0.000 description 10
- 230000006870 function Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000004087 circulation Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000012840 feeding operation Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 238000012913 prioritisation Methods 0.000 description 1
Classifications
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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
- F15B13/025—Pressure reducing valves
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
- F15B21/087—Control strategy, e.g. with block diagram
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- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Servomotors (AREA)
Abstract
The invention belongs to hydraulic servo control system fields, a kind of double nargin SERVO CONTROL valve groups of low throttling noise, including 3-position-3-way hydraulic directional valve, 2/2-way electro-hydraulic reversing valve, check valve, main servo valve, standby servo valve, two six logical electro-hydraulic reversing valves, repairing check valve, control module, throttle valves are provided.The present invention is integrated by the combination of the Hydraulic Elements such as 3-position-3-way hydraulic directional valve, 2/2-way electro-hydraulic reversing valve, check valve, two six logical electro-hydraulic reversing valves, realize the redundancy backup of servo valve, realize the loaded self-adaptive variation of P mouthfuls of pressure of servo valve, the steering engine displacement closed-loop control of larger Exceed load can be completed by realizing relatively low charge oil pressure, reduce the pressure difference of servo valve valve port in the case of Exceed load, the throttling noise for reducing control valve group, reduces energy loss.
Description
Technical field
The invention belongs to hydraulic servo control system fields, and in particular to a kind of double nargin SERVO CONTROLs of low throttling noise
Valve group.
Background technology
SERVO CONTROL valve group generally comprises servo valve and other auxiliary hydraulic pressure elements, is mainly used for hydraulic servo steering engine system
Control, realize steering engine hydraulic cylinder displacement closed loop.
Current SERVO CONTROL valve group is using constant pressure source as power source, and hydraulic cylinder is in larger Exceed load（Hydraulic cylinder
The direction of load force is identical as hydraulic cylinder direction）Under the action of, the pressure difference at servo valve valve port both ends is very in control valve group
Greatly, cause throttling noise larger.In addition, under smaller loading condition, the pressure of constant pressure source can be higher by load very much, steering engine hydraulic pressure
When cylinder closed-loop control, the pressure difference at servo valve valve port both ends is equally big, meanwhile, energy loss is also big.
Invention content
The purpose of the present invention is to overcome the above deficiencies in the prior art, and provides a kind of low throttling noise
Double nargin SERVO CONTROL valve groups, the reliability of control valve group can be effectively improved, the control valve group have redundancy backup while,
The pressure of servo valve pressure oil port can be according to the situation of change of load, and the automatic oil sources adapted to of choosing is as power source.Load
When larger, servo valve pressure oil port chooses high-voltage power supply as power source, in the case of loading relatively low or Exceed load, servo valve pressure
Power hydraulic fluid port chooses low pressure source as power source, to reduce the pressure difference of valve port, reduces throttling noise, while can also reduce energy
Amount loss.
The present invention solve its technical problem the technical solution adopted is that：A kind of double nargin pilot valves of low throttling noise
Group, including 3-position-3-way hydraulic directional valve, 2/2-way electro-hydraulic reversing valve, the first check valve, main servo valve, repairing check valve,
Control module, throttle valve；
The 3-position-3-way hydraulic directional valve belt spool Displacement Feedback, P, T mouth of the 3-position-3-way hydraulic directional valve with height
Pressure oil source communicates, and A mouthfuls communicate with the P of 2/2-way electro-hydraulic reversing valve mouths, and hydraulic control mouth is connected with A, B of hydraulic cylinder mouth respectively；
The initial bit of the 2/2-way electro-hydraulic reversing valve is conducting position, and A mouths and the master of the 2/2-way electro-hydraulic reversing valve watch
The P mouths for taking valve communicate；The 2/2-way electro-hydraulic reversing valve realizes commutation under the action of controlling signal；
The main servo valve belt spool Displacement Feedback, P mouthfuls are communicated by the first check valve with low pressure oil sources, A, B mouthfuls and liquid
A, B mouth of cylinder pressure are connected, and the T mouths of main servo valve are connected with throttle valve；The main servo valve is realized in the case where controlling signal function
The displacement closed-loop control of hydraulic cylinder, while feeding back spool displacement signal；
The repairing check valve quantity is 2, B mouthfuls of A, B mouths for connecing main servo valve respectively, A mouthfuls with the T mouths of main servo valve
It is connected；The function of repairing check valve is to realize the repairing of A, B mouthfuls of servo valve under Exceed load operating mode.
The control module include power supply, CPU, analog input output module and I 0 module, the analog input
Output module is connected with active and standby valve core of servo valve and 3-position-3-way hydraulic directional valve spool, the I 0 module and 2/2-way electricity
Liquid reversal valve is connected, and the control module is fed back by acquiring main servo valve core and 3-position-3-way hydraulic directional valve spool displacement
Signal, judges whether Exceed load, so control 2/2-way electro-hydraulic reversing valve electric or dead electricity, when Exceed load, two
Two logical electro-hydraulic reversing valves of position obtain electric, otherwise dead electricity；
Described throttle valve one end is connected with the T of main servo valve mouths, and one end is connected with fuel tank, and function is to make T mouthfuls of generations of servo valve
Certain back pressure realizes multi-level throttle, reduces throttling noise.
First check valve, the second check valve function be realize high pressure fuel source and low pressure oil sources one-way isolation.
Double nargin SERVO CONTROL valve groups of further prioritization scheme, low throttling noise further include standby servo valve and two six
Logical electro-hydraulic reversing valve, the standby servo valve arrangement is identical as main servo valve, the P mouthfuls of P by the second check valve and main servo valve
Mouth communicates, while the P mouths and the P mouths of 2/2-way electro-hydraulic reversing valve and the A mouth phases of 3-position-3-way hydraulic directional valve of standby servo valve
Logical, the T mouths of standby servo valve are communicated with the T of main servo valve mouths；The pressure oil port and oil return opening of described two six logical electro-hydraulic reversing valves
It is communicated respectively with A, B of active and standby servo valve mouth, A, B mouth of two six logical electro-hydraulic reversing valves are connected with A, B of hydraulic cylinder mouth.
In above-mentioned technical proposal, the main servo valve, standby servo valve and two six logical electro-hydraulic reversing valves complete servo valve
Redundancy backup, described two six logical electro-hydraulic reversing valves complete the switching of active and standby servo valve oil circuit by commutating.
In the above-mentioned technical solutions, the 3-position-3-way hydraulic directional valve is the reversal valve of symmetrical structure function, i.e. spool
It turns left identical with post exercise function of turning right.For 3-position-3-way hydraulic directional valve at middle position, reversal valve is in cut-off position；Work as spool
After opening to a certain degree（Load is more than certain value, which can be set by parameter designing）, reversal valve is in the conduction state, realizes
High pressure fuel source is to servo valve oil feeding line unimpeded.
A kind of double nargin SERVO CONTROL valve groups of low throttling noise provided by the invention, utilize 3-position-3-way hydraulic directional valve
And main servo valve P in the case of the loaded self-adaptive and Exceed load of 2/2-way electro-hydraulic reversing valve realization P mouthfuls of pressure of main servo valve
The function that mouth pressure switches to low pressure oil sources.When original state, 3-position-3-way hydraulic directional valve is in middle position, and 2/2-way is electro-hydraulic
Reversal valve is in initial bit, when main servo valve steering, just loading it is lower in the case of, underloading is to overcome 3-position-3-way to surge
The spring force of reversal valve makes 3-position-3-way hydraulic directional valve open, and main servo valve P mouthfuls of pressure source is provided by low pressure oil sources at this time.
In the case of Exceed load, 2/2-way electro-hydraulic reversing valve obtains electric, and it is much no matter to load absolute value at this time, P mouthfuls of main servo valve
Pressure by low pressure oil sources provide.Just loading it is larger in the case of, load overcome the spring force of 3-position-3-way hydraulic directional valve to make
3-position-3-way hydraulic directional valve is opened, and main servo valve P mouthfuls of pressure source is provided by high pressure fuel source at this time, meanwhile, as load increases
Greatly, 3-position-3-way hydraulic directional valve valve core opening increases, and high pressure fuel source is also smaller by the restriction loss of the valve, main servo valve P
The pressure of mouth is also bigger, that is, has adapted to the variation of load.
For the P mouths of servo valve directly with three in a kind of double nargin SERVO CONTROL valve groups of low throttling noise provided by the invention
The A mouths of position three-way hydraulic reversal valve communicate, and the variation of the pressure adaptation load of P mouthfuls of servo valve, that is, when loading big, P may be implemented
Confession oil pressure is big, and load is low, and P confession oil pressures are low, meanwhile, it avoids 2/2-way electro-hydraulic reversing valve clamping stagnation and cannot achieve
The defect that the valve control of high load manipulates, improves the reliability of valve group.
The invention has the advantages that by 3-position-3-way hydraulic directional valve, 2/2-way electro-hydraulic reversing valve, check valve,
The combination of the Hydraulic Elements such as two six logical electro-hydraulic reversing valves is integrated, realizes the redundancy backup of servo valve, realizes P mouthfuls of servo valve
The loaded self-adaptive of pressure changes, and the steering engine displacement closed loop control of larger Exceed load can be completed by realizing relatively low charge oil pressure
System, reduces the pressure difference of servo valve valve port in the case of Exceed load, reduces the throttling noise of control valve group, reduces energy damage
Consumption.
Description of the drawings
Fig. 1 is the principle schematic of the embodiment of the present invention.
In figure：1 3-position-3-way hydraulic directional valve, 2 2/2-way electro-hydraulic reversing valves, 3 second check valves, 4 main servo valves, 5
Standby servo valve, 6 two six logical electro-hydraulic reversing valves, 7 repairing check valves, 8 control modules, 9 throttle valves, 10 first check valves.
Fig. 2 is 3-position-3-way hydraulic directional valve original state structural schematic diagram in embodiment.
Fig. 3 is critical open state structural schematic diagram when 3-position-3-way hydraulic directional valve spool moves right in embodiment.
Fig. 4 is 3-position-3-way hydraulic directional valve fully open state structural schematic diagram in embodiment.
Specific implementation mode
The invention will be further described below in conjunction with the accompanying drawings.
As shown in Figure 1, the embodiment of the present invention provides a kind of double nargin SERVO CONTROL valve groups of low throttling noise, including three
Three-way hydraulic reversal valve 1,2/2-way electro-hydraulic reversing valve 2, the second check valve 3, main servo valve 4, standby servo valve 5, two six are logical
Electro-hydraulic reversing valve 6, repairing check valve 7, control module 8, throttle valve 9, the first check valve 10.
1 belt spool Displacement Feedback of the 3-position-3-way hydraulic directional valve, P, T mouth of the 3-position-3-way hydraulic directional valve 1
It is communicated with high pressure fuel source, the A mouths of 3-position-3-way hydraulic directional valve 1 are communicated with the P of 2/2-way electro-hydraulic reversing valve 2 mouths, three
The hydraulic control mouth of three-way hydraulic reversal valve 1 is connected with A, B of hydraulic cylinder mouth respectively；
The initial bit of the 2/2-way electro-hydraulic reversing valve 2 is conducting position, A mouths and the master of the 2/2-way electro-hydraulic reversing valve 2
The P mouths of servo valve 4 communicate；The 2/2-way electro-hydraulic reversing valve 2 realizes commutation under the action of controlling signal；
4 belt spool Displacement Feedback of the main servo valve, P mouthfuls are communicated by the first check valve 10 with low pressure oil sources, main servo valve 4
A, B mouth communicated with two six logical electro-hydraulic reversing valves 6, the T mouths of main servo valve 4 are connected with throttle valve；The main servo valve 4 is being controlled
The displacement closed-loop control of hydraulic cylinder is realized under signal function processed, while feeding back spool displacement signal；
5 structure of the standby servo valve is identical as main servo valve 4, the P mouthfuls of P mouth phases by the second check valve 3 and main servo valve 4
It is logical, while the P mouths and the P mouths of 2/2-way electro-hydraulic reversing valve 2 and the A mouth phases of 3-position-3-way hydraulic directional valve 1 of standby servo valve 5
Logical, T mouthfuls communicate with the T of main servo valve 4 mouths；
The pressure oil port and oil return opening of described two six logical electro-hydraulic reversing valves 6 are communicated with A, B of active and standby servo valve mouth respectively, and two
A, B mouth of six logical electro-hydraulic reversing valves 6 of position are connected with A, B of hydraulic cylinder mouth；
7 quantity of repairing check valve is 2, B mouthfuls of A, B mouths for connecing two six logical electro-hydraulic reversing valves 6 respectively, repairing check valve
7 A mouths are connected with the T of active and standby servo valve mouths；
The control module include power supply, CPU, analog input output module and I 0 module, the analog input output
Module is connected with active and standby valve core of servo valve and 3-position-3-way hydraulic directional valve spool, the I 0 module with 2/2-way is electro-hydraulic changes
It is connected to valve, the control module is fed back by acquiring active and standby valve core of servo valve and 3-position-3-way hydraulic directional valve spool displacement
Signal, judges whether Exceed load, so control 2/2-way electro-hydraulic reversing valve electric or dead electricity, when Exceed load, two
Two logical electro-hydraulic reversing valves of position obtain electric, otherwise dead electricity；
Described throttle valve one end is connected with the T of active and standby servo valve mouths, and the other end is connected with fuel tank.
For ease of the elaboration of operation principle, such as given a definition：
a）Two cavity pressure of hydraulic cylinder indicates with Pa and Pb respectively, load pressure Pf=Pa-Pb；
b）3-position-3-way hydraulic directional valve spool displacement indicates that valve core of servo valve displacement is indicated with z with x, spool, hydraulic cylinder displacement
Dextrad is just that left-hand is negative.
The operation principle of double nargin SERVO CONTROL valve groups of low throttling noise includes two large divisions, the redundancy backup of servo valve
And low throttling noise principle.
a）The redundancy backup of servo valve
When original state, A, B mouth of main servo valve 4 are communicated with A, B of hydraulic cylinder mouth, and A, B mouth cut-off of standby servo valve 5, master watch
Take the control that valve 4 carries out hydraulic cylinder；When two six logical electro-hydraulic reversing valves 6 obtain electric, A, B of A, B mouth and hydraulic cylinder of standby servo valve 5
Mouth communicates, and A, B mouth cut-off of main servo valve 4, standby servo valve 5 carry out the control of hydraulic cylinder.
b）Low throttling noise operation principle
1）Pa is more than Pb, and hydraulic cylinder moves right（Positive load behavior）
When Pa is more than Pb, and hydraulic cylinder moves right（For example hydraulic cylinder is moved right from zero-bit, and load is overcome to do work）, three
Three-way hydraulic reversal valve 1 spool in position moves right under the differential pressure action of Pa and Pb, and the 3-position-3-way that control module 8 acquires surges
1 spool displacement x of reversal valve is that just, 4 spool displacement z of main servo valve is negative, and control module 8 is to 2/2-way electro-hydraulic reversing valve at this time
The 2 control signals sent are 0, i.e. dead electricity.
If Pf（Pa-Pb）Less than setting value, 1 spool displacement of 3-position-3-way hydraulic directional valve is not big enough（Valve as shown in Figure 3
Core location status）, high pressure fuel source PH still can not be by the restriction of spool, at this point, the P mouths pressure of main servo valve 4 is only at this time
It is communicated with low pressure oil sources PL, i.e. P mouthfuls of pressure is low pressure, at this point, main servo valve 4 carries out valve control in the case of low pressure oil sources fuel feeding
Operation.
When Pf is greater than the set value, load pressure Pf is enough to overcome the spring force of 3-position-3-way hydraulic directional valve 1, makes spool
A and PH mouthfuls communicate（As shown in Figure 4）, PH mouthfuls of high pressure oil pass through 3-position-3-way hydraulic directional valve 1 at this time and 2/2-way is electric
Liquid reversal valve 2 is to the P confession high pressure oils of main servo valve 4, simultaneously as the effect of the first check valve 10, P mouthfuls of high pressure oils are without normal direction
PL mouthfuls of circulations, in the case, the P mouth pressure of main servo valve 4 automatically switches to high pressure oil system, in addition, as load is pressed
The valve core opening amount of the increase of power, 3-position-3-way hydraulic directional valve 1 increases, and PH passes through 1 spool of 3-position-3-way hydraulic directional valve
The pressure loss reduces, and the P mouth pressure of main servo valve 4 gradually increases with load pressure at this time, plays the role of loaded self-adaptive.
2）Pa is more than Pb, and hydraulic cylinder moves downward（Exceed load operating mode）
a）When Pa is more than Pb, and hydraulic cylinder moves downward（For example hydraulic cylinder is moved from right position maximum value to zero-bit, load drives
Hydraulic cylinder）, 1 spool of 3-position-3-way hydraulic directional valve pressure Pa and Pb effect under be moved to the left, control module 8 acquire
1 spool displacement x of 3-position-3-way hydraulic directional valve is that just, 4 spool displacement z of main servo valve is just that control module 8 is to two two at this time
The control signal that logical electro-hydraulic reversing valve 2 is sent is 1, i.e. 2/2-way electro-hydraulic reversing valve 2 obtains electric.
b）If Pf is less than setting value, 1 spool displacement of 3-position-3-way hydraulic directional valve is not big enough（Spool as shown in Figure 3
Location status）, high pressure fuel source PH still can not be by the restriction of spool, at this point, the pressure of P mouthfuls of servo valve and low pressure at this time
Oil sources PL is communicated, i.e. P mouthfuls of pressure is low pressure, and main servo valve 4 carries out valve control operation in the case of low pressure oil sources fuel feeding.
c）When Pf is greater than the set value, load pressure is larger at this time, and is enough to overcome 1 spring of 3-position-3-way hydraulic directional valve
Power makes A and PH mouthfuls of spool communicate（As shown in Figure 4）, but 2/2-way electro-hydraulic reversing valve 2 is in left position, A mouthfuls of high pressures at this time
Oil can not be by 2/2-way electro-hydraulic reversing valve 2 to the P confession high pressure oils of main servo valve 4, in the case, the P of main servo valve 4
Mouthful pressure only communicated with low pressure oil sources PL, i.e. P mouthful pressure is low pressure, main servo valve 4 in the case of low pressure oil sources fuel feeding into
Valve control operation in the case of row Exceed load, reduces the P mouths of main servo valve 4 and B mouthfuls of pressure difference.
3）Pb is more than Pa
Operation principle is identical more than Pb as Pa at this time（Because 1 or so working position of 3-position-3-way hydraulic directional valve is identical）, institute's difference
Be that Pa is more than Pb when, 3-position-3-way hydraulic directional valve 1 is operated in left position, when pb is more than Pa, 1 work of 3-position-3-way hydraulic directional valve
Make in right position.
In conclusion the above is merely preferred embodiments of the present invention, being not intended to limit the scope of the present invention.
Said program is one kind of this patent example, and the solenoid directional control valve of the hydraulic directional valve congenerous of congenerous replaces still capable of
The institute for having reached cost instance is functional.The present invention cannot be only used for steering gear system displacement closed-loop control, apply also for realizing other
Position-force control in Hydrauservo System.
The content not being described in detail in this specification belongs to the prior art well known to those skilled in the art.
Claims (3)
1. a kind of double nargin SERVO CONTROL valve groups of low throttling noise, it is characterized in that：Including 3-position-3-way hydraulic directional valve, two
Two logical electro-hydraulic reversing valves, the first check valve, main servo valve, repairing check valve, control module, throttle valve；
The 3-position-3-way hydraulic directional valve belt spool Displacement Feedback, P, T mouth of the 3-position-3-way hydraulic directional valve with height
Pressure oil source communicates, and the A mouths of 3-position-3-way hydraulic directional valve are communicated with the P of 2/2-way electro-hydraulic reversing valve mouths, and 3-position-3-way surges
The hydraulic control mouth of reversal valve is connected with A, B of hydraulic cylinder mouth respectively；
The initial bit of the 2/2-way electro-hydraulic reversing valve is conducting position, and A mouths and the master of the 2/2-way electro-hydraulic reversing valve watch
The P mouths for taking valve communicate；The 2/2-way electro-hydraulic reversing valve realizes commutation under the action of controlling signal；
The main servo valve belt spool Displacement Feedback, P mouthfuls are communicated by the first check valve with low pressure oil sources, the A of main servo valve,
B mouthfuls are connected with A, B of hydraulic cylinder mouth, and the T mouths of main servo valve are connected with throttle valve；The main servo valve is in control signal function
It is lower to realize the displacement closed-loop control of hydraulic cylinder, while feeding back spool displacement signal；
The repairing check valve quantity is 2, B mouthfuls of A, B mouths for connecing main servo valve respectively, A mouths and the master of repairing check valve
The T mouths of servo valve are connected；
The control module is electric control module, by acquiring main servo valve core and 3-position-3-way hydraulic directional valve spool position
Move feedback signal, judge whether Exceed load, so control 2/2-way electro-hydraulic reversing valve electric or dead electricity, work as Exceed load
When, 2/2-way electro-hydraulic reversing valve obtains electric, otherwise dead electricity；
Described throttle valve one end is connected with the T of main servo valve mouths, and the other end is connected with fuel tank.
2. double nargin SERVO CONTROL valve groups of low throttling noise according to claim 1, it is characterized in that：Including standby servo valve
With two six logical electro-hydraulic reversing valves, the standby servo valve arrangement is identical as main servo valve, and P mouthfuls are watched by the second check valve and master
The P mouths for taking valve communicate, while the P mouths and 3-position-3-way hydraulic directional valve of the P mouths and 2/2-way electro-hydraulic reversing valve of standby servo valve
A mouths communicate, the T mouths of standby servo valve are communicated with the T of main servo valve mouths；The pressure oil port of described two six logical electro-hydraulic reversing valves and
Oil return opening is communicated with A, B of active and standby servo valve mouth respectively, A, B mouth of two six logical electro-hydraulic reversing valves and A, B mouth phase of hydraulic cylinder
Connection.
3. double nargin SERVO CONTROL valve groups of low throttling noise according to claim 2, it is characterized in that：The control module
Including power supply, CPU, analog input output module and I 0 module, the analog input output module and active and standby servo
Valve core and 3-position-3-way hydraulic directional valve spool are connected, the I 0 module be connected with 2/2-way electro-hydraulic reversing valve.
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| CN201810284178.1A CN108317117B (en) | 2018-04-02 | 2018-04-02 | Double-margin servo control valve group with low throttle noise |
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Citations (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2645215A2 (en) * | 1987-10-05 | 1990-10-05 | Rexroth Mannesmann Gmbh | LOAD INDEPENDENT CONTROL DEVICE FOR HYDRAULIC USER DEVICES |
| JP2001027203A (en) * | 1999-07-12 | 2001-01-30 | Hitachi Constr Mach Co Ltd | Directional control valve device with hydraulic regenerative circuit |
| CN201078362Y (en) * | 2006-12-14 | 2008-06-25 | 天津市华泰森淼生物工程技术有限公司 | Hydraulic pressure control system of integration supervoltage biological treatment equipment |
| CN101532517A (en) * | 2009-04-10 | 2009-09-16 | 长春理工大学 | Method for simulating servo system load by electrohydraulic servo |
| CN202250059U (en) * | 2011-06-03 | 2012-05-30 | 中国船舶重工集团公司第七○五研究所高技术公司 | Pump suction-draining device for formation tester |
| CN102513413A (en) * | 2011-12-03 | 2012-06-27 | 南京埃尔法电液技术有限公司 | Hydraulic control system for novel servo pump control bending machine |
| CN103148041A (en) * | 2013-03-07 | 2013-06-12 | 北京理工大学 | Energy-saving active/passive load double electrohydraulic servo valve control system and control method thereof |
| CN104295551A (en) * | 2014-08-18 | 2015-01-21 | 中国农业大学 | Self-steering proportional control valve block and navigation hydraulic system based on self-steering proportional control valve block |
| CN104564885A (en) * | 2015-01-08 | 2015-04-29 | 宁波宇洲液压科技有限公司 | High-integration bidirectional rotary valve for pilot control mode |
| WO2015117338A1 (en) * | 2014-02-10 | 2015-08-13 | 太原理工大学 | Single-hydraulic motor double-loop control system |
| DE102015209074B3 (en) * | 2015-05-18 | 2016-08-25 | Danfoss Power Solutions Gmbh & Co. Ohg | DEVICE AND METHOD FOR CONTROLLING A HYDRAULIC MACHINE |
| EP3104022A1 (en) * | 2015-06-12 | 2016-12-14 | National Oilwell Varco Norway AS | Improvements in the control of hydraulic actuators |
| CA2955713A1 (en) * | 2015-10-27 | 2017-04-27 | China University Of Mining And Technology | A multi-cylinder synchronous energy-saving and efficient hydraulic lift system and method thereof |
| CN106939909A (en) * | 2017-05-10 | 2017-07-11 | 吉林大学 | A kind of hydraulic auxiliary driving system of integrated hydraulic starter |
| CN208138231U (en) * | 2018-04-02 | 2018-11-23 | 中国船舶重工集团公司第七一九研究所 | A kind of double nargin SERVO CONTROL valve groups of low throttling noise |
-
2018
- 2018-04-02 CN CN201810284178.1A patent/CN108317117B/en active Active
Patent Citations (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2645215A2 (en) * | 1987-10-05 | 1990-10-05 | Rexroth Mannesmann Gmbh | LOAD INDEPENDENT CONTROL DEVICE FOR HYDRAULIC USER DEVICES |
| JP2001027203A (en) * | 1999-07-12 | 2001-01-30 | Hitachi Constr Mach Co Ltd | Directional control valve device with hydraulic regenerative circuit |
| CN201078362Y (en) * | 2006-12-14 | 2008-06-25 | 天津市华泰森淼生物工程技术有限公司 | Hydraulic pressure control system of integration supervoltage biological treatment equipment |
| CN101532517A (en) * | 2009-04-10 | 2009-09-16 | 长春理工大学 | Method for simulating servo system load by electrohydraulic servo |
| CN202250059U (en) * | 2011-06-03 | 2012-05-30 | 中国船舶重工集团公司第七○五研究所高技术公司 | Pump suction-draining device for formation tester |
| CN102513413A (en) * | 2011-12-03 | 2012-06-27 | 南京埃尔法电液技术有限公司 | Hydraulic control system for novel servo pump control bending machine |
| CN103148041A (en) * | 2013-03-07 | 2013-06-12 | 北京理工大学 | Energy-saving active/passive load double electrohydraulic servo valve control system and control method thereof |
| WO2015117338A1 (en) * | 2014-02-10 | 2015-08-13 | 太原理工大学 | Single-hydraulic motor double-loop control system |
| CN104295551A (en) * | 2014-08-18 | 2015-01-21 | 中国农业大学 | Self-steering proportional control valve block and navigation hydraulic system based on self-steering proportional control valve block |
| CN104564885A (en) * | 2015-01-08 | 2015-04-29 | 宁波宇洲液压科技有限公司 | High-integration bidirectional rotary valve for pilot control mode |
| DE102015209074B3 (en) * | 2015-05-18 | 2016-08-25 | Danfoss Power Solutions Gmbh & Co. Ohg | DEVICE AND METHOD FOR CONTROLLING A HYDRAULIC MACHINE |
| EP3104022A1 (en) * | 2015-06-12 | 2016-12-14 | National Oilwell Varco Norway AS | Improvements in the control of hydraulic actuators |
| CA2955713A1 (en) * | 2015-10-27 | 2017-04-27 | China University Of Mining And Technology | A multi-cylinder synchronous energy-saving and efficient hydraulic lift system and method thereof |
| CN106939909A (en) * | 2017-05-10 | 2017-07-11 | 吉林大学 | A kind of hydraulic auxiliary driving system of integrated hydraulic starter |
| CN208138231U (en) * | 2018-04-02 | 2018-11-23 | 中国船舶重工集团公司第七一九研究所 | A kind of double nargin SERVO CONTROL valve groups of low throttling noise |
Non-Patent Citations (2)
| Title |
|---|
| 陈彬,易孟林: "电液伺服阀的研究现状和发展趋势", 液压与气动, no. 06 * |
| 顾建,叶菊芳,吴彤: "电液伺服阀静态性能试验台", 实验技术与管理, no. 02 * |
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