CN106122123A - The Electro-hydraulic Servo System of a kind of exportable dynamic pressure and agglomerating plant - Google Patents
The Electro-hydraulic Servo System of a kind of exportable dynamic pressure and agglomerating plant Download PDFInfo
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- CN106122123A CN106122123A CN201610809490.9A CN201610809490A CN106122123A CN 106122123 A CN106122123 A CN 106122123A CN 201610809490 A CN201610809490 A CN 201610809490A CN 106122123 A CN106122123 A CN 106122123A
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- valve
- directional control
- solenoid directional
- control valve
- hydraulic
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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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
-
- 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
-
- 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
-
- 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
Abstract
The present invention discloses the Electro-hydraulic Servo System of a kind of exportable dynamic pressure, comprising: oil cylinder；Drive motor, hydraulic pump；Described driving motor is connected with hydraulic pump, and described driving driven by motor hydraulic pump action is by the oil extraction of oil cylinder；First check valve；It is connected with described hydraulic pump oil-out；Electrohydraulic servo valve, the first solenoid directional control valve；Described electrohydraulic servo valve P mouth and the first check valve are connected, and A mouth is connected with described first solenoid directional control valve P mouth；3rd solenoid directional control valve, its P mouth and the first solenoid directional control valve oil-out connect；Described 3rd solenoid directional control valve is connected with upper hydraulic cylinder；4th solenoid directional control valve, its P mouth and the first solenoid directional control valve oil-out connect；Described 4th solenoid directional control valve is connected with lower hydraulic cylinder.
Description
Technical field
The present invention relates to technical field of hydraulic pressure, particularly relate to a kind of exportable dynamic pressure Electro-hydraulic Servo System and
Agglomerating plant.
Background technology
For the metal that pottery and some fusing point are higher, hot pressed sintering is generally used to prepare in sintering preparation process
Method.
Hot pressed sintering refers to, while to pottery or metal dust high-temperature heating, apply unidirectional or two-way to powder
Pressure, the densification process of powder quick material.But in existing hot-press sintering equipment, due to single underground structure
Under the constraint of the hydraulic system become, hydraulic system is only provided that constant pressure (i.e. static pressure).Work at such static pressure
Under with, granule is difficult to sliding rearrangement, pore is difficult to discharge, and is difficult to eliminate " hard aggregation " formed between granule, is easily caused microcosmic
The non-uniform phenomenon of structure, thus have impact on consistency and the mechanical property of sintered material.The hydraulic pressure system of usual pressure sintering furnace
The constant pressure that system is provided leverages the range of sintering furnace, constrains hot-pressed sintering furnace and prepares higher performance advanced person
The probability of material.
Summary of the invention
The technical problem to be solved is, for the above-mentioned deficiency of prior art, proposes one and is applicable to
Agglomerating plant exports the electro-hydraulic servo drive hydraulic system principle of dynamic pressure.It optimizes design by the driving of electrohydraulic servo valve
Connection line accurately, forms multiple different hydraulic circuit, it is achieved frequency and the output of the controlled dynamic pressure of waveform.This liquid
Pressure system is applied in high-temperature sintering apparatus, can be applicable to prepare the pottery of the high-quality performances such as high density, low defect, high intensity and
The materials such as hard alloy.
The present invention solves its technical problem and employed technical scheme comprise that, proposes the electro-hydraulic servo of a kind of exportable dynamic pressure
Hydraulic system, comprising:
Oil cylinder；
Drive motor, hydraulic pump；Described driving motor is connected with hydraulic pump, and described driving driven by motor hydraulic pump action will
The oil extraction of oil cylinder；
First check valve；It is connected with described hydraulic pump oil-out；
Electrohydraulic servo valve, the first solenoid directional control valve；Described electrohydraulic servo valve P mouth and the first check valve are connected, and A mouth is with described
First solenoid directional control valve P mouth is connected；
3rd solenoid directional control valve, its P mouth and the first solenoid directional control valve oil-out connect；Described 3rd solenoid directional control valve is with upper
Hydraulic cylinder connects；
4th solenoid directional control valve, its P mouth and the first solenoid directional control valve oil-out connect；Described 4th solenoid directional control valve with under
Hydraulic cylinder connects.
Further, also including the second solenoid directional control valve, its P mouth and the first check valve are connected；Described second electromagnetic switch
Valve oil-out is connected with the 3rd solenoid directional control valve and the 4th solenoid directional control valve P mouth the most respectively.
Further, also include accumulator, be connected with the first check valve.
Further, overflow valve and cooler are also included；Described hydraulic pump oil-out is connected with overflow valve, described overflow valve
It is connected with cooler.
Further, first throttle valve and the second throttling it are also associated with between described 3rd solenoid directional control valve and upper hydraulic cylinder
Valve；Described first throttle valve partners with second throttle and superposes choke valve；Described first throttle valve and upper hydraulic cylinder oil-feed
Crossing connects, and described second throttle is connected with upper hydraulic cylinder oil return crossing.
Further, it is connected between described 4th solenoid directional control valve with lower hydraulic cylinder cavity of resorption oil circuit and has the first unidirectional sequence
Valve.
Further, on described electrohydraulic servo valve, connection has the first electric driver controlling electro-hydraulic servo threshold switch, institute
State to connect on the first solenoid directional control valve and have the second electric driver controlling its commutation, described 3rd solenoid directional control valve connects and has
Control it and be positioned at left position or the 4th electric driver of right position and the 5th electric driver, described 4th solenoid directional control valve connects
It is positioned at left position or the 6th electric driver of right position and the 7th electric driver control.
Further, on described second solenoid directional control valve, connection has the 3rd electric driver controlling its commutation.
Further, described upper hydraulic cylinder lower end and lower hydraulic cylinder upper end are provided with limit switch.
Invention additionally discloses a kind of agglomerating plant, it includes the Electro-hydraulic Servo System of above-mentioned exportable dynamic pressure.
The present invention has the advantages that compared to existing technology
By controlling the opening and closing state of electrohydraulic servo valve and combining the state of each solenoid directional control valve and make the present invention
Hydraulic system can be at automatically and two kinds of mode of operations of crawl.When electrohydraulic servo valve is opened, by electrohydraulic servo valve front end
Instruction output, makes hydraulic system in strict accordance with instruction output frequency and the controlled dynamic pressure of amplitude through servo amplifier.
By the hydraulic system applications of this exportable dynamic pressure in agglomerating plant now, sinterable go out the higher material of performance.
Accompanying drawing explanation
Fig. 1 is the structural representation of Electro-hydraulic Servo System in a preferred embodiment of the present invention.
Detailed description of the invention
The following is the specific embodiment of the present invention and combine accompanying drawing, technical scheme is further described,
But the present invention is not limited to these embodiments.
Refer to Fig. 1, in the present embodiment, the Electro-hydraulic Servo System of exportable dynamic pressure, it includes fuel tank 1, drives
Galvanic electricity machine 2, hydraulic pump the 3, first check valve the 4, first filter the 5, second filter the 6, the 3rd filter 7, forced air cooler 8, storage
Can device the 9, first Pressure gauge the 10, second Pressure gauge 11, electrohydraulic servo valve the 12, first solenoid directional control valve the 13, second solenoid directional control valve
14, the 3rd solenoid directional control valve the 15, the 4th solenoid directional control valve 16, pressure transducer 17, first throttle valve 18, second throttle 19,
First overflow valve the 20, first one way sequence valve 21, upper hydraulic cylinder 22, lower hydraulic cylinder 23, upper limit position switch 24, lower position switch
25。
In above-mentioned Hydraulic Elements, fuel tank 1, driving motor 2, hydraulic pump the 3, first check valve 4, electrohydraulic servo valve 12, first
Solenoid directional control valve the 13, the 3rd solenoid directional control valve the 15, the 4th solenoid directional control valve 16, upper hydraulic cylinder 22, lower hydraulic cylinder 23 constitute this
Apply for the core parts in the servo-drive loop of exportable dynamic pressure.
Its mode of operation is as follows: open electrohydraulic servo valve 12, starts and drives motor 2, and hydraulic oil flows out from fuel tank 1 oil-out
After filter through the first filter 5 and pass through hydraulic pump 3 and pump into the first check valve 4, hydraulic oil is a road after the first check valve 4
Electrohydraulic servo valve 12P mouth is flowed into through the second filter 6.Electrohydraulic servo valve 12A mouth accesses the first electricity after connecting the 3rd filter 7
Magnetic reversal valve 13P mouth.The oil-out of the first solenoid directional control valve 13 flows out to the 3rd solenoid directional control valve 15 simultaneously and the 4th electromagnetism changes
To the P mouth of valve 16.
3rd solenoid directional control valve 15 after the superposition choke valve being made up of first throttle valve 18 and second throttle 19 with
Upper hydraulic cylinder 22 connects.Wherein first throttle valve 18 is connected with the oil-feed crossing of upper hydraulic cylinder 22, second throttle 19 and upper liquid
The oil return crossing of cylinder pressure 22 connects.In the present embodiment, owing to being provided with superposition choke valve, can be big by the opening of regulation choke valve
Little to control or the uninterrupted of the upper hydraulic cylinder oil circuit of regulation, and then control the movement velocity of upper hydraulic cylinder piston.
It is connected between 4th solenoid directional control valve 16 with lower hydraulic cylinder 23 cavity of resorption oil circuit and has the first one way sequence valve 21.First is single
Make lower hydraulic cylinder 23 cavity of resorption form the pressure balanced each other with lower hydraulic cylinder moiety by weight to sequence valve 21, can be prevented it
Gliding because of deadweight, now the effect of hydraulic lock is played in balanced loop.
Inputted by the instruction of electrohydraulic servo valve 12 front end, and amplify through servo amplifier so that system is in automatically
Mode of operation, can make system in strict accordance with instruction output frequency and the controlled dynamic pressure of amplitude.
In addition to above-mentioned automatic operation mode, the hydraulic system of the present embodiment also can realize crawl mode of operation.
Wherein, fuel tank 1, driving motor 2, hydraulic pump the 3, first check valve the 4, second solenoid directional control valve the 14, the 3rd electromagnetism change
The core parts of crawl mode of operation are constituted to valve the 15, the 4th solenoid directional control valve 16, upper hydraulic cylinder 22, lower hydraulic cylinder 23.
In crawl mode of operation, need to close electrohydraulic servo valve 12.First check valve 4 separates a road and changes with the second electromagnetism
Connecting to the P mouth of valve 14, the oil-out of the second solenoid directional control valve 14 is respectively connecting to the 3rd solenoid directional control valve 15 and the 4th electromagnetism
The P mouth of reversal valve 16.In crawl mode of operation, can be switched by control panel point operation control, realize upper and lower hydraulic cylinder respectively
Individually upper and lower displacement work.
In a preferred embodiment, the first check valve 4 also separates a road binders road and is connected with accumulator 9.When having a power failure or hydraulic pressure
Pump occurs when failure and other reasons makes hydraulic power source lose efficacy, and the first check valve 4 cuts off downward oil circuit, and available accumulator 9 carries out safety
Operation, still can be to hydraulic cylinder fuel feeding.
In a preferred embodiment, hydraulic pump 3 oil-out is also connected with overflow valve 20, and is also associated with wind on overflow valve 20
Cooler 8.During system is run, regulation relief valve 20 can change the output pressure of hydraulic pump 3, when the regulation pressure of overflow valve 20
After determining, hydraulic pump 3 just works under the regulation pressure of overflow valve 20, and overflow valve plays level pressure overflow effect, to keep system pressure
Power is stable, and is not affected by loading not change, it is achieved thereby that hydraulic system to be carried out pressure regulation and voltage stabilizing control, overflow valve 20
Set pressure should wherein comprise the various pressure losses on pipeline more than the maximum working pressure (MWP) of hydraulic cylinder.
In a preferred embodiment, the lower end of upper hydraulic cylinder and the upper end of lower hydraulic cylinder all devise a limit switch,
The displacement stroke preventing hydraulic cylinder is excessive, affects the properly functioning of hydraulic cylinder.
In the present embodiment, electrohydraulic servo valve 12 connects and has the first electric driver controlling electro-hydraulic servo threshold switch
YV1；First solenoid directional control valve 13 connects and has the second electric driver YV2 controlling its commutation；At the second solenoid directional control valve
Connect on 14 and have the 3rd electric driver YV3 controlling its commutation；On the 3rd solenoid directional control valve connect have control its be positioned at a left side
Position or the 4th electric driver YV4 and the 5th electric driver YV5 of right position；4th solenoid directional control valve connects have and control it
It is positioned at the 6th electric driver YV6 and the 7th electric driver YV7 of left position or right position.
Duty below in conjunction with components and parts each in Electro-hydraulic Servo System describes native system in detail in work automatically
Operation principle under pattern and crawl mode of operation.
(1) automatic operation mode
When table 1 shows hydraulic system automatic operation mode, the action norm table of hydraulic system, illustrates this in conjunction with this table
The electro-hydraulic servo drive hydraulic system principle of bright exportable dynamic pressure operation principle under automatic operation mode.
Table 1:
Under hydraulic system automatic operation mode, can by drive motor 2, electrohydraulic servo valve the 12, first solenoid directional control valve 13,
3rd solenoid directional control valve the 15, the 4th solenoid directional control valve 16, first throttle valve 18, first throttle valve 19 and the first one way sequence valve
21, in conjunction with upper hydraulic cylinder 22 and lower hydraulic cylinder 23, build servo-drive loop, by the instruction output of servo valve front end, through watching
Take amplifier, make system in strict accordance with instruction output frequency and the controlled dynamic pressure of amplitude.
Under hydraulic system automatic operation mode, the electric driver YV3 of the second solenoid directional control valve must not be electric, liquid in fuel tank 1
Force feed enters electrohydraulic servo valve 12 through hydraulic pump the 3, first check valve 4, and now YV1 obtains electric, and electrohydraulic servo valve 12 works, P mouth and A
Mouth is connected, and hydraulic oil enters the first solenoid directional control valve 13 through A mouth, and YV2 obtains electric work, the P mouth of the first solenoid directional control valve 13 and B
Mouth connection, hydraulic oil separates two fluid path through oil-out B mouth, respectively enters the 3rd solenoid directional control valve 15 and the 4th solenoid directional control valve
The oil inlet P mouth of 16, under this automatic operation mode, upper and lower hydraulic cylinder works simultaneously.
During pressurization protocols, YV4, YV7 all electric, the 3rd solenoid directional control valve 15 is in left position, and P mouth connects with A mouth, B mouth and T
Mouth connection, hydraulic oil is entered by P mouth, and A mouth goes out, then enters the rodless cavity of upper hydraulic cylinder 22 through first throttle valve 18, has bar in cylinder
The fluid in chamber returns to T mouth through second throttle 19, and the 4th solenoid directional control valve 16 is in right position, and P mouth connects with B mouth, A mouth and T
Mouth connection, hydraulic oil is entered by P mouth, and B mouth goes out, and enters the rodless cavity of lower hydraulic cylinder 23, rod chamber in cylinder through the first sequence valve 21
Fluid return to T mouth, it is descending that upper hydraulic cylinder 22 piston rod drags workpiece, and lower hydraulic cylinder 23 piston rod drags on workpiece
OK, upper and lower hydraulic cylinder all stretches out, and by regulating the openings of sizes of first throttle valve 18, just can control or regulate the stream of upper cylinder half oil circuit
Amount size, and then control the movement velocity of upper hydraulic cylinder 22 piston so that it is keep one with the movement velocity of lower hydraulic cylinder 23 piston
Causing, ensure that pressure process is steadily carried out, now YV3, YV5, YV6 all must not electricity.
During blood pressure lowering program, YV5, YV6 all electric, the 3rd solenoid directional control valve 15 is in right position, and P mouth connects with B mouth, A mouth and T
Mouth connection, hydraulic oil is entered by P mouth, and B mouth goes out, then enters the rodless cavity of upper hydraulic cylinder 22 through first throttle valve 19, has bar in cylinder
The fluid in chamber returns to T mouth through second throttle 19, and the 4th solenoid directional control valve 16 is in left position, and P mouth connects with A mouth, B mouth and T
Mouth connection, hydraulic oil is entered by P mouth, and A mouth goes out, and it is up that upper hydraulic cylinder 22 piston rod drags workpiece, lower hydraulic cylinder 23 piston
Bar drag workpiece descending, upper and lower hydraulic cylinder is all retracted, by regulate second throttle 19 openings of sizes, just can control or
The uninterrupted of regulation upper cylinder half oil circuit, and then control the movement velocity of upper hydraulic cylinder 22 piston so that it is with lower hydraulic cylinder 23 piston
Movement velocity keep consistent, ensure that pressure reduction is steadily carried out, now YV3, YV4, YV7 all must not electricity.
Electrohydraulic servo valve 12 front end comprises servo amplifier, and the instruction that instrument transmits enters electro-hydraulic watching through servo amplifier
Taking valve 12, according to the characteristic frequency provided and the dynamic pressure signal of telecommunication of amplitude, the openings of sizes controlling electrohydraulic servo valve realizes
Flow-control, switching electric driver YV4, YV5, YV6 and YV7 obtains dead electricity program simultaneously, and then is reflected in upper and lower hydraulic cylinder
In displacement, pressure transducer 17 is positioned on the oil-in front end oil circuit of the 3rd solenoid directional control valve 15 and solenoid directional control valve 16, in real time
Upper and lower cylinder pressure under writing task pattern, can make regulation of hydraulic system export by arranging different waveforms and amplitude
The dynamic pressure of particular requirement.
(2) crawl mode of operation
When table 2 shows hydraulic system crawl mode of operation, the action norm table of hydraulic system, illustrates this in conjunction with this table
The electro-hydraulic servo drive hydraulic system principle of bright exportable dynamic pressure operation principle under crawl mode of operation.
Table 2:
In crawl mode of operation, when hydraulic system starts, driving motor 2 to work, the electric driver YV8 of overflow valve 20 obtains
Electricity, and other electric drivers all must not be electric, hydraulic pump 3, overflow valve 20, cooler 8 constitute simple circuit, the first Pressure gauge 10
Display hydraulic pump 3 pressure, hydraulic cylinder attonity.
In crawl mode of operation, by closedown and the unlatching of electric driver, it is achieved the real-time displacement of hydraulic cylinder moves up and down
Make.Now, electric driver YV1 and YV2 the most all must not be electric, and electric driver YV3 obtains electric, and the second electromagnetism changes
In valve 14, P mouth connects with B mouth, and hydraulic oil enters through the first filter 5, hydraulic pump the 3, first check valve 4 through fuel tank 1 oil-out
Enter the oil inlet P mouth of the second solenoid directional control valve 14, oil-out B mouth be respectively communicated with the 3rd solenoid directional control valve 15 and the 4th electromagnetism changes
To the oil inlet P mouth of valve.Under crawl mode of operation, upper and lower hydraulic cylinder works independently.
When YV4 obtains electric, the 3rd solenoid directional control valve 15 is in left position, and P mouth connects with A mouth, and B mouth connects with T mouth, hydraulic oil by
P mouth enters, and A mouth goes out, then enters the rodless cavity of upper hydraulic cylinder 22 through first throttle valve 18, and in cylinder, the fluid of rod chamber is through second
Choke valve 19 returns to T mouth, and it is descending that upper hydraulic cylinder 22 piston rod drags workpiece, and upper hydraulic cylinder stretches out, and downstream rate is by first
Choke valve 18 aperture regulates, and now YV1, YV2, YV5, YV6, YV7 all must not electricity.
When YV5 obtains electric, the 3rd solenoid directional control valve 15 is in right position, and P mouth connects with B mouth, and A mouth connects with T mouth, hydraulic oil by
P mouth enters, and B mouth goes out, then enters the rod chamber of upper hydraulic cylinder 22 through second throttle 19, and in cylinder, the fluid of rodless cavity is through first
Choke valve 18 returns to T mouth, and it is up that upper hydraulic cylinder 22 piston rod drags workpiece, and upper hydraulic cylinder is retracted, and speed uplink is by second
Choke valve 19 aperture regulates, and now YV1, YV2, YV4, YV6, YV7 all must not electricity.
When YV6 obtains electric, the 4th solenoid directional control valve 16 is in left position, and P mouth connects with A mouth, and B mouth connects with T mouth, hydraulic oil by
P mouth enters, and A mouth goes out, and enters back into the rod chamber of lower hydraulic cylinder 23, and in cylinder, the fluid of rodless cavity is through the first one way sequence valve 21 times
To T mouth, it is descending that lower hydraulic cylinder 23 piston rod drags workpiece, and lower hydraulic cylinder 23 is retracted, and oil return line also exists certain back of the body
Pressure, suitably regulates the unlatching pressure of one way sequence valve 21, the back of the body galassing that when lower hydraulic cylinder 23 can be made to decline, the rod chamber of cylinder produces
Weighing apparatus piston deadweight, adjusts to support the workpiece deadweights such as piston by this back pressure, and piston just can smoothly fall, and prevents from surpassing
Speed decline has an accident and cavitation, and now YV1, YV2, YV4, YV5, YV7 all must not electricity.
When YV7 obtains electric, the 4th solenoid directional control valve 16 is in right position, and P mouth connects with B mouth, and A mouth connects with T mouth, hydraulic oil by
P mouth enters, and B mouth goes out, and enters the rodless cavity of lower hydraulic cylinder 23 through the first sequence valve 21, and in cylinder, the fluid of rod chamber returns to T mouth, under
Hydraulic cylinder 23 piston rod dragging workpiece is up, and lower hydraulic cylinder stretches out, and now YV1, YV2, YV4, YV5, YV6 all must not electricity；
When the 4th solenoid directional control valve 16 is in middle position, owing to having added an one way sequence valve 21 on the cavity of resorption oil circuit of lower cylinder, make down
Cylinder cavity of resorption formation one and the pressure of lower cylinder motion parts balanced, can prevent it from gliding because of deadweight, now balance back
The effect of hydraulic lock is played on road.
In sum, the electro-hydraulic servo of exportable dynamic pressure be applicable to agglomerating plant of the present embodiment drives hydraulic pressure system
System, by the driving of electrohydraulic servo valve, connects multiple Hydraulic Elements, optimizes and design connection line accurately, form multiple difference
Hydraulic circuit, design novel dynamic pressure electro-hydraulic servo drive hydraulic system principle, frequency and controlled dynamic of waveform can be realized
The output of pressure, this hydraulic system applications is in agglomerating plant, by the introducing of dynamic pressure, solves microcosmic in sintering process
The non-uniform phenomenon of structure, has widened the range of sintering furnace significantly, can prepare the high-qualitys such as high density, low defect, high intensity
The advanced material of performance.
The application is also disclosed a kind of agglomerating plant, and it includes above-mentioned hydraulic system.
Specific embodiment described herein is only to present invention spirit explanation for example.Technology neck belonging to the present invention
Described specific embodiment can be made various amendment or supplements or use similar mode to replace by the technical staff in territory
Generation, but without departing from the spirit of the present invention or surmount scope defined in appended claims.
Claims (10)
1. the Electro-hydraulic Servo System of an exportable dynamic pressure, it is characterised in that: including:
Oil cylinder；
Drive motor, hydraulic pump；Described driving motor is connected with hydraulic pump, and described driving driven by motor hydraulic pump action is by oil cylinder
Oil extraction；
First check valve；It is connected with described hydraulic pump oil-out；
Electrohydraulic servo valve, the first solenoid directional control valve；Described electrohydraulic servo valve P mouth and the first check valve are connected, A mouth and described first
Solenoid directional control valve P mouth is connected；
3rd solenoid directional control valve, its P mouth and the first solenoid directional control valve oil-out connect；Described 3rd solenoid directional control valve and upper hydraulic pressure
Cylinder connects；
4th solenoid directional control valve, its P mouth and the first solenoid directional control valve oil-out connect；Described 4th solenoid directional control valve and lower hydraulic pressure
Cylinder connects.
Electro-hydraulic Servo System the most according to claim 1, it is characterised in that: also include the second solenoid directional control valve, its P
Mouth is connected with the first check valve；Described second solenoid directional control valve oil-out changes with the 3rd solenoid directional control valve and the 4th electromagnetism the most respectively
Connect to valve P mouth.
Electro-hydraulic Servo System the most according to claim 1 and 2, it is characterised in that: also include accumulator, single with first
Connect to valve.
Electro-hydraulic Servo System the most according to claim 1 and 2, it is characterised in that: also include overflow valve and cooler；
Described hydraulic pump oil-out is connected with overflow valve, and described overflow valve is connected with cooler.
Electro-hydraulic Servo System the most according to claim 1, it is characterised in that: described 3rd solenoid directional control valve and upper liquid
First throttle valve and second throttle it is also associated with between cylinder pressure；Described first throttle valve partners with second throttle and superposes
Choke valve；Described first throttle valve is connected with upper hydraulic cylinder oil-feed crossing, described second throttle and upper hydraulic cylinder oil return crossing
Connect.
Electro-hydraulic Servo System the most according to claim 1, it is characterised in that: described 4th solenoid directional control valve and lower liquid
Connect between cylinder pressure cavity of resorption oil circuit and have the first one way sequence valve.
Electro-hydraulic Servo System the most according to claim 1, it is characterised in that: connect on described electrohydraulic servo valve and have control
First electric driver of electro-hydraulic servo threshold switch processed, described first solenoid directional control valve connects and has the second electricity controlling its commutation
Driving means, described 3rd solenoid directional control valve connects have and controls it and be positioned at the 4th electric driver and the 5th of left position or right position
Electric driver, described 4th solenoid directional control valve connects to be had control it is positioned at left position or the 6th electric driver of right position and the
Seven electric drivers.
8. according to the Electro-hydraulic Servo System described in claim 2 or 7, it is characterised in that: on described second solenoid directional control valve
Connect and have the 3rd electric driver controlling its commutation.
Electro-hydraulic Servo System the most according to claim 1, it is characterised in that: described upper hydraulic cylinder lower end and lower hydraulic pressure
Cylinder upper end is provided with limit switch.
10. an agglomerating plant, it is characterised in that: include exportable dynamic pressure as described in any one of claim 1-9
Electro-hydraulic Servo System.
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| JPH10156599A (en) * | 1996-11-25 | 1998-06-16 | Amada Co Ltd | Hydraulic actuation device in press machine |
| CN103775399A (en) * | 2014-01-24 | 2014-05-07 | 北京交通大学 | Hydraulic system for tunnel loading test platform |
| CN105317763A (en) * | 2014-10-23 | 2016-02-10 | 武汉理工大学 | Electro hydraulic servo system for high-frequency fine-blanking forming equipment |
| CN104444707A (en) * | 2014-10-30 | 2015-03-25 | 中国矿业大学 | Ultra-deep vertical shaft hoist steel wire rope tension balancing system and method |
| CN105066682A (en) * | 2015-08-05 | 2015-11-18 | 清华大学 | Rapid-densification pressure-coupling dynamic sintering furnace and sintering method |
| CN105135873A (en) * | 2015-08-05 | 2015-12-09 | 清华大学 | Dynamic pressure electric pulse double-field control sintering furnace and sintering method |
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