CN107842530A - A kind of hydraulic system of high speed drift - Google Patents
A kind of hydraulic system of high speed drift Download PDFInfo
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- CN107842530A CN107842530A CN201711202856.7A CN201711202856A CN107842530A CN 107842530 A CN107842530 A CN 107842530A CN 201711202856 A CN201711202856 A CN 201711202856A CN 107842530 A CN107842530 A CN 107842530A
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- displacement pump
- hydraulic cylinder
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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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/16—Control arrangements for fluid-driven presses
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
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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 kind of hydraulic system of high speed drift, mainly include low pressure constant displacement pump, high pressure constant displacement pump, motor, low pressure sequences valve, high pressure sequence valve, the first check valve, second check valve, high pressure accumulator, low pressure accumulator, hydraulic control two-way valve, the 3rd check valve, threeway hydraulic servovalve, triple valve, connecting plate, drift hydraulic cylinder, threeway hydraulic servovalve mainly include three-way control valve, position feedback loop, valve element driving hydraulic cylinder.The function that the present invention has the commutation of drift mechanical hydraulic servo and just double pressure independently switch with load, the high speed stroke of hydraulic punching head and fast run-up pressure can be realized, energy consumption is low, punch stroke can adjust, punching precision is high, and its mesolow constant displacement pump, high pressure constant displacement pump, motor are integrated into power unit, and remaining component is integrated into execution unit, the pipeline of whole system is simple, integrated level is high, has good stability.
Description
Technical field
The present invention relates to a kind of hydraulic system, more particularly to a kind of hydraulic system of high speed drift.
Background technology
High speed drift is used to quickly charge and attack out variously-shaped, size hole or part on a metal plate, has very high
Operating efficiency and larger blanking pressure, therefore the fluid power system of high speed drift must possess high speed stroke and fast run-up pressure energy
Power, in addition, how optimizing on the premise of the quick motion of guarantee with the output of big blanking pressure, reducing energy consumption is also in design high-speed punching
The key issue that must take into consideration during the hydraulic system of head, otherwise not only results in the waste of the energy, adjoint heating problem can also
Cause hydraulic work system unstable so that the reliability decrease of high speed drift.
The content of the invention
It is an object of the invention to provide a kind of hydraulic system of high speed drift, it can realize that drift is completed on a metal plate
It is efficient to charge and attack operation；The efficiency of simultaneity factor is high, heating is few, possesses excellent job stability.
Technical scheme is as follows：
The invention mainly comprises low pressure constant displacement pump, high pressure constant displacement pump, motor, low pressure sequences valve, high pressure sequence valve, first unidirectional
Valve, the second check valve, high pressure accumulator, low pressure accumulator, hydraulic control two-way valve, the 3rd check valve, tee joint machine-hydraulic servo, three
Port valve, connecting plate, drift hydraulic cylinder.
Further, tee joint machine-hydraulic servo of the present invention mainly includes three-way control valve, position feedback loop, valve element
Driving hydraulic cylinder, the valve element of three-way control valve are connected as an entirety, position feedback loop with the piston rod of valve element driving hydraulic cylinder
It is installed on the piston rod of valve element driving hydraulic cylinder, position of the position feedback loop on valve element driving hydraulic cylinder piston rod can adjust
Section.
Further, low pressure constant displacement pump of the present invention and the high pressure constant displacement pump are coaxial serial dual pump, the low pressure
The discharge capacity of constant displacement pump is more than the discharge capacity of the high pressure constant displacement pump, and the motor drives the low pressure constant displacement pump and the height simultaneously
Press constant displacement pump.
Further, oil inlet, the height of the oil-out of low pressure constant displacement pump of the present invention and the low pressure sequences valve
Press the oil inlet connection of the oil-out, first check valve of sequence valve, oil-out and the high pressure of the high pressure constant displacement pump
The oil inlet connection of the oil inlet of sequence valve, second check valve, the high pressure accumulator go out with second check valve
Hydraulic fluid port, the control port of the high pressure sequence valve, the hydraulic control two-way valve A mouths connection, the low pressure accumulator with it is described low
Press the control port of sequence valve, the oil-out of first check valve, a control mouths of the hydraulic control two-way valve, the 3rd list
The rod chamber connection of the P mouths of oil inlet, the triple valve to valve, the drift hydraulic cylinder, the B mouths of the hydraulic control two-way valve with
The P mouths connection of the oil-out, the three-way control valve of 3rd check valve, A mouths and the hydraulic control of the three-way control valve
The rodless cavity connection of the b control mouths of two-port valve, the drift hydraulic cylinder, A mouths and the valve element driving hydraulic pressure of the triple valve
The rodless cavity connection of cylinder, the oil inlet of the low pressure constant displacement pump, the oil inlet of the high pressure constant displacement pump, the low pressure sequences valve
Oil-out, the T mouths of the three-way control valve, the T mouths of the triple valve connect with hydraulic oil container.
Further, the big I consecutive variations of the valve port of triple valve of the present invention, when the valve element of the triple valve commutates
Between can adjust, have a machine feedback push rod on the valve element of the triple valve, the triple valve also has reversing handle, possesses hand
Dynamic commutation function.
Further, drift hydraulic cylinder of the present invention is used to drive drift, the piston rod of the drift hydraulic cylinder and institute
The cylinder body for stating valve element driving hydraulic cylinder is connected as an entirety by the connecting plate, and the triple valve is fixedly installed in the valve
The cylinder body of core driving hydraulic cylinder, piston rod, the triple valve, the cylinder body of the valve element driving hydraulic cylinder of the drift hydraulic cylinder
Three moves together, and the machine feedback push rod of the triple valve can contact or depart from the position feedback loop.
Beneficial effects of the present invention are as follows：
1st, the present invention controls the commutation of drift hydraulic cylinder by machine-liquid servo control mechanism, realizes the stroke commutation fortune of drift high speed
It is dynamic, and movement travel can adjust.
2nd, the height-low double pressure systems independently switched with load change in the present invention ensure that the rapidity for building pressure, simultaneously
Optimize system energy efficiency.
3rd, the control intervention that the present invention in the course of the work need not be extraneous, can realize that the high frequency time of high speed drift charges and attacks
Action, energy consumption is low, and heating is few, and use reliability is high.
4th, integrated level of the present invention is high, is easily installed, safeguards and maintenance.
Brief description of the drawings
Fig. 1 is the hydraulic principle schematic diagram of the present invention.
Fig. 2 is the principle schematic of tee joint machine-hydraulic servo in the present invention.
The low pressure of hydraulic oil quickly sweeps away the stage and flows to schematic diagram when Fig. 3 is present invention work.
The high pressure of hydraulic oil sweeps away the stage and flows to schematic diagram when Fig. 4 is present invention work.
The backhaul stage of hydraulic oil flows to schematic diagram when Fig. 5 is present invention work.
In Fig. 1：1- low pressure constant displacement pumps, 2- high pressure constant displacement pumps, 3- motor, 4- low pressure sequences valves, 5- high pressure sequence valves, 6-
First check valve, the check valves of 7- second, 8- high pressure accumulators, 9- low pressure accumulators, 10- hydraulic control two-way valves, 11- the 3rd are unidirectional
Valve, 12- tee joint machines-hydraulic servo, 13- triple valves, 14- connecting plates, 15- drift hydraulic cylinders.
In Fig. 2：12.1- three-way control valves, 12.2- position feedback loops, 12.3- valve element driving hydraulic cylinders.
Embodiment
The present invention is further illustrated below in conjunction with the accompanying drawings.
Referring to Fig. 1, the invention mainly comprises：Low pressure constant displacement pump 1, high pressure constant displacement pump 2, motor 3, low pressure sequences valve 4, height
Press sequence valve 5, the first check valve 6, the second check valve 7, high pressure accumulator 8, low pressure accumulator 9, hydraulic control two-way valve the 10, the 3rd single
To valve 11, tee joint machine-hydraulic servo 12, triple valve 13, connecting plate 14, drift hydraulic cylinder 15.
Referring to Fig. 2, tee joint machine-hydraulic servo 12 of the present invention mainly includes：Three-way control valve 12.1, position feedback loop
12.2nd, valve element driving hydraulic cylinder 12.3, the valve element of three-way control valve 12.1 are connected with the piston rod of valve element driving hydraulic cylinder 12.3
For an entirety, position feedback loop 12.2 is installed on the piston rod of valve element driving hydraulic cylinder 12.3, and position feedback loop 12.2 exists
Position on the piston rod of valve element driving hydraulic cylinder 12.3 can be adjusted.
Referring to Fig. 1, low pressure constant displacement pump 1 of the present invention and the high pressure constant displacement pump 2 are coaxial serial dual pump, the low pressure
The discharge capacity of constant displacement pump 1 is more than the discharge capacity of the high pressure constant displacement pump 2, and the motor 3 drives the low pressure constant displacement pump 1 and institute simultaneously
State high pressure constant displacement pump 2.
Referring to Fig. 1, Fig. 2, the oil inlet of the oil-out of low pressure constant displacement pump 1 of the present invention and the low pressure sequences valve 4, institute
State the oil inlet connection of the oil-out, first check valve 6 of high pressure sequence valve 5, the oil-out of the high pressure constant displacement pump 2 and institute
The oil inlet connection of the oil inlet, second check valve 7 of high pressure sequence valve 5 is stated, the high pressure accumulator 8 is single with described second
The control port of oil-out, the high pressure sequence valve 5 to valve 7, the A mouths connection of the hydraulic control two-way valve 10, the low pressure store
Can device 9 and the control port of the low pressure sequences valve 4, the oil-out of first check valve 6, a of the hydraulic control two-way valve 10
Control mouth, the oil inlet of the 3rd check valve 11, the P mouths of the triple valve 13, the rod chamber of the drift hydraulic cylinder 15 connect
Logical, the B mouths of the hydraulic control two-way valve 10 connect with the oil-out of the 3rd check valve 11, the P mouths of the three-way control valve 12.1
It is logical, the b control mouths of the A mouths of the three-way control valve 12.1 and the hydraulic control two-way valve 10, the drift hydraulic cylinder 15 without bar
Chamber connects, and the A mouths of the triple valve 13 connect with the rodless cavity of the valve element driving hydraulic cylinder 12.3, the low pressure constant displacement pump 1
Oil inlet, the oil inlet of the high pressure constant displacement pump 2, the oil-out of the low pressure sequences valve 4, the three-way control valve 12.1
T mouths, the T mouths of the triple valve 13 connect with hydraulic oil container.
The big I consecutive variations of valve port of triple valve 13 of the present invention, the valve element commutating period of the triple valve 13 is adjustable
Save, have a machine feedback push rod on the valve element of the triple valve 13, the triple valve 13 also has reversing handle, possesses manually
Commutation function.
Referring to Fig. 1, Fig. 2, drift hydraulic cylinder 15 of the present invention is used to drive drift, the piston rod of drift hydraulic cylinder 15 with
The cylinder body of the valve element driving hydraulic cylinder 12.3 is connected as an entirety by the connecting plate 14, and the triple valve 13 fixes peace
Cylinder body loaded on the valve element driving hydraulic cylinder 12.3, piston rod, the triple valve 13, the valve of the drift hydraulic cylinder 15
The cylinder body three of core driving hydraulic cylinder 12.3 moves together, and the machine feedback push rod of the triple valve 13 can contact or depart from institute
State position feedback loop 12.2.
Referring to Fig. 3-5, the course of work of the invention can be divided into that low pressure is quickly swept away, high pressure is swept away, backhaul three phases,
These three stages are that circulation is carried out successively.Heavy line represents running of hydraulic power oil direction in Fig. 3-5.
Referring to Fig. 3-5, when low pressure quickly sweeps away the stage and started, the piston of drift hydraulic cylinder 15 is in up stroke terminal, liquid
Control two-port valve 10 is in cut-off state, and high pressure accumulator 8 maintains the pressure of the control mouth of high pressure sequence valve 5, and high pressure sequence valve 5 is in
Conducting state, the machine feedback push rod of the valve element of triple valve 13 contact with position feedback loop 12.2, and triple valve 13 is in P mouths and A mouths
Connected with maximum open, the state of T mouths cut-off, the piston rod of valve element driving hydraulic cylinder 12.3 is completely out by hydraulic oil, threeway
Control valve 12.1 is in the state that P mouths are connected with A mouths with maximum open, T mouths end, because the valve element row of three-way control valve 12.1
Journey is far smaller than the stroke of drift hydraulic cylinder 15, thus the machine feedback push rod of the valve element of triple valve 13 and position feedback loop 12.2 this
Shi Buhui departs from, and the rod chamber of drift hydraulic cylinder 15 is through the 3rd check valve 11, three-way control valve 12.1 and drift hydraulic cylinder
15 rodless cavity is connected so as to form differential circuit, and the hydraulic oil that high pressure constant displacement pump 2 exports is determined by high pressure sequence valve 5 with low pressure
Measure the hydraulic oil that pump 1 exports to collaborate, the hydraulic oil behind interflow enters differential time of drift hydraulic cylinder 15 by the first check valve 6
Road, now drift not yet contact load, the piston rod of drift hydraulic cylinder 15 are stretched out with prestissimo.
The stage is quickly swept away in low pressure, hydraulic oil has certain when flowing through the 3rd check valve 11, three-way control valve 12.1
The pressure loss, so for pressure slightly larger than at b control mouths, hydraulic control two-way valve 10 maintains cut-off at a control mouths of hydraulic control two-way valve 10
State.
The stage is quickly swept away in low pressure, the piston rod of drift hydraulic cylinder 15, triple valve 13, valve element driving hydraulic cylinder 12.3
Cylinder body three moves downwardly together as an entirety, and the machine feedback push rod of the valve element of triple valve 13 will be when moving downward one section
Between after depart from position feedback loop 12.2, at this moment the valve element of triple valve 13 pushes another working position to by spring, valve element commutation
During the state change of the valve port of triple valve 13 be：P mouths are connected with A mouths with maximum open, the connection of T mouths cut-off → P mouths and A mouths
Opening is gradually reduced, T mouths cut-off → P mouths cut-off, the open communication of A mouths and T mouths gradually increase → cut-off of P mouths, A mouths and T mouths with
Maximum open connects, because the valve element commutation of triple valve 13 needs the throttling action of regular hour and valve port, valve element driving
Pressure in the rodless cavity of hydraulic cylinder 12.3 gradually reduces, therefore the commutation that the valve element of three-way control valve 12.1 is promoted by spring
Process is fed back also in gradually being completed in a period of time, rather than in the machine feedback push rod of triple valve 13 valve element with position
Ring 12.2 commutates immediately when departing from, and the state change of the valve port of three-way control valve 12.1 is in valve element commutation process：P mouths and A mouths
Connected with maximum open, the open communication of T mouths cut-off → P mouths and A mouths is gradually reduced, the T mouths cut-off → cut-off of P mouths, A mouths and T mouths
Open communication gradually increase → P mouths cut-off, A mouths connected with T mouths with maximum open, three at the end of low pressure quickly sweeps away the stage
The state of the logical valve port of control valve 12.1 is connected for P mouths with A mouths with smaller opening, the cut-off of T mouths, and the state of the valve port of triple valve 13 is P
Mouth cut-off, A mouths are connected with T mouths with smaller opening.
When punch. contact workpiece, drift hydraulic cylinder 15 make it that pressure increases in rodless cavity by load effect, of the invention
The course of work sweeps away the stage into high pressure.
Referring to Fig. 3-5, the stage is swept away in high pressure, pressure has bar higher than drift hydraulic cylinder 15 in the rodless cavity of drift hydraulic cylinder 15
Cavity pressure, then pressure is more than at a control mouths at the b control mouths of hydraulic control two-way valve 10, and hydraulic control two-way valve 10 switches to connection
State, in high pressure accumulator 8 hydraulic oil outflow cause the pressure of the control mouth of high pressure sequence valve 5 to decline, high pressure sequence valve 5 ends,
The hydraulic oil that high pressure constant displacement pump 2 exports flows into drift liquid by the second check valve 7, hydraulic control two-way valve 10, three-way control valve 12.1
The rodless cavity of cylinder pressure 15, the 3rd check valve 11 isolates low-pressure hydraulic oil with high pressure liquid force feed, from the rod chamber of drift hydraulic cylinder 15
The hydraulic oil of outflow enters low pressure accumulator 9 and causes the pressure of the control mouth of low pressure sequences valve 4 to increase, and low pressure sequences valve 4 turns on, low
The hydraulic oil that pressure constant displacement pump 1 exports directly flows back to fuel tank, and the valve port of three-way control valve 12.1 is in P at the end of high pressure sweeps away the stage
Near the critical condition that mouth, A mouths, T mouths are turned off, the state of the valve port of triple valve 13 is the cut-off of P mouths, A mouths and T mouths with maximum open
Connection.
When low pressure quickly sweeps away the stage and started, liquid that hydraulic oil that high pressure constant displacement pump 2 exports, low pressure constant displacement pump 1 export
Force feed, the hydraulic oil from the outflow of the rod chamber of drift hydraulic cylinder 15 collaborate, and the hydraulic oil behind interflow flows through three-way control valve 12.1, this
When three-way control valve 12.1 valve port state connected with A mouths with maximum open for P mouths；The stage is swept away in high pressure, only high pressure quantifies
The hydraulic oil that pump 2 exports flows through three-way control valve 12.1, now the valve port state of three-way control valve 12.1 be P mouths and A mouths with compared with
Small open communication；The discharge capacity of high pressure constant displacement pump 2 is less than low pressure constant displacement pump 1.In summary, the threeway control in the course of work of the present invention
The open state of valve 12.1 processed matches with the uninterrupted flowed through.
After drift is completed to charge and attack, pressure has discharged in the rodless cavity of drift hydraulic cylinder 15, and the course of work of the invention is entered
Enter the backhaul stage.
Referring to Fig. 3-5, when the backhaul stage starts, the valve port state of three-way control valve 12.1 is the cut-off of P mouths, A mouths and T mouths
Open communication gradually increase, pressure is gradually shed in the rodless cavity of drift hydraulic cylinder 15, at the b control mouths of hydraulic control two-way valve 10
Pressure is less than hydraulic control two-way valve 10 when at a control mouths, and switchback cut-off state, the hydraulic oil that high pressure constant displacement pump 2 exports are filled with height again
Accumulator 8, the control mouth pressure rise of high pressure sequence valve 5 are pressed, high pressure sequence valve 5 turns on again, the liquid that high pressure constant displacement pump 2 exports
Press oil the hydraulic oil exported with low pressure constant displacement pump 1 again to collaborate, the hydraulic oil behind interflow enters drift hydraulic pressure through the first check valve 6
The rod chamber of cylinder 15, the piston rod of drift hydraulic cylinder 15 are quickly withdrawn, and the hydraulic oil flowed out from the rodless cavity of drift hydraulic cylinder 15 is through three
Logical control valve 12.1 flows back to fuel tank.
In the backhaul stage, the piston rod of drift hydraulic cylinder 15, triple valve 13, the cylinder body three of valve element driving hydraulic cylinder 12.3
Moved upwardly together as an entirety, the machine feedback push rod of the valve element of triple valve 13 will after motion a period of time upwards with position
Put feedback loop 12.2 to contact again, the valve element of triple valve 13 is pushed back original working position by machine feedback bar, at this moment triple valve 13
The state change of valve port is：The cut-off of P mouths, A mouths and T mouths connect with maximum open → open communication of the cut-off of P mouths, A mouths and T mouths by
Decrescence small → P mouths gradually increase with the open communication of A mouths, T mouths cut-off → P mouths are connected with A mouths with maximum open, the cut-off of T mouths, together
Sample is because the valve element commutation of triple valve 13 needs the throttling action of regular hour and valve port, the nothing of valve element driving hydraulic cylinder 12.3
Pressure in rod cavity gradually rises, therefore the valve element of three-way control valve 12.1 gradually drives liquid within a period of time by valve element
The piston rod of cylinder pressure 12.3 pushes back, rather than when the machine feedback push rod of the valve element of triple valve 13 contacts with position feedback loop 12.2
Commutate immediately, the state change of the valve port of three-way control valve 12.1 is in valve element commutation process：The cut-off of P mouths, A mouths and T mouths are with most
The open communication of big opening connection → P mouths cut-off, A mouths and T mouths is gradually reduced → and the open communication of P mouths and A mouths gradually increases, T
Mouth cut-off → P mouths are connected with A mouths with maximum open, the cut-off of T mouths, the shape of the valve port of three-way control valve 12.1 at the end of the backhaul stage
State is that P mouths are connected with A mouths with maximum open, T mouths end, and the state of the valve port of triple valve 13 is connected for P mouths with A mouths with maximum open
Logical, T mouths cut-off, at this moment three-way control valve 12.1, the valve port state of triple valve 13 are that low pressure quickly sweeps away the stage when starting
State.
Stage and backhaul stage are quickly swept away in low pressure, low pressure constant displacement pump 1 closes with the hydraulic oil that high pressure constant displacement pump 2 exports
Stream, system are in big flow, operating on low voltage state；Stage, the 1 complete release of low pressure constant displacement pump are swept away in high pressure, only high pressure quantifies
The output hydraulic pressure of pump 2 oil, system are in low discharge, high-pressure work state.By matching high and low pressure and low pressure constant displacement pump 1, high pressure
The discharge capacity of constant displacement pump 2, system power invariability in whole working cycle process can be made, thus the redundancy of power is not present in system
Or waste.
High pressure accumulator 8 replace with low pressure accumulator 9 in whole efforts cyclic process fill, tapping force feed, enter one
Step improves the movement velocity of drift hydraulic cylinder 15.
To charge and attack stroke be the valve element machine feedback by position feedback loop 12.2 and triple valve 13 for drift hydraulic cylinder 15 reciprocal
What the relative motion distance between push rod determined, this relative motion distance can be by adjusting position feedback loop 12.2 in valve element
Position on the piston rod of driving hydraulic cylinder 12.3 changes.
The lasting reciprocating reversing motion of drift hydraulic cylinder 15 needs the change and threeway control of the direction of motion of drift hydraulic cylinder 15
Certain synchronization association is kept between the commutation of the valve element of valve 12.1 processed, the regulation of this synchronization association is then by matching threeway
The valve element commutating period of valve 13 is realized with valve port area gradient.
The manual reverse of direction function of triple valve 13 is used for emergency disposal.
Mesolow constant displacement pump of the present invention, high pressure constant displacement pump, motor can be integrated into power unit, and remaining component can be integrated into
Execution unit, pipeline is simple between power unit and execution unit.Whole system integrated level is high, and installation, dismounting and replacing are convenient,
Be advantageous to the maintenance and maintenance of system.
Claims (4)
1. a kind of hydraulic system of high speed drift, it is characterized in that：Mainly include low pressure constant displacement pump（1）, high pressure constant displacement pump（2）, electricity
Motivation（3）, low pressure sequences valve（4）, high pressure sequence valve（5）, the first check valve（6）, the second check valve（7）, high pressure accumulator
（8）, low pressure accumulator（9）, hydraulic control two-way valve（10）, the 3rd check valve（11）, tee joint machine-hydraulic servo（12）, triple valve
（13）, connecting plate（14）, drift hydraulic cylinder（15）；The low pressure constant displacement pump（1）With the high pressure constant displacement pump（2）For coaxial series connection
Double pump, the low pressure constant displacement pump（1）Discharge capacity be more than the high pressure constant displacement pump（2）Discharge capacity, the motor（3）Drive simultaneously
The low pressure constant displacement pump（1）With the high pressure constant displacement pump（2）；The low pressure constant displacement pump（1）Oil-out and the low pressure sequences
Valve（4）Oil inlet, the high pressure sequence valve（5）Oil-out, first check valve（6）Oil inlet connection, the height
Press constant displacement pump（2）Oil-out and the high pressure sequence valve（5）Oil inlet, second check valve（7）Oil inlet connection,
The high pressure accumulator（8）With second check valve（7）Oil-out, the high pressure sequence valve（5）Control port, described
Hydraulic control two-way valve（10）A mouths connection, the low pressure accumulator（9）With the low pressure sequences valve（4）Control port, described
One check valve（6）Oil-out, the hydraulic control two-way valve（10）A control mouths, the 3rd check valve（11）Oil inlet, institute
State triple valve（13）P mouths, the drift hydraulic cylinder（15）Rod chamber connection, the hydraulic control two-way valve（10）B mouths and institute
State the 3rd check valve（11）Oil-out, tee joint machine-hydraulic servo（12）Three-way control valve（12.1）P mouths connection, it is described
Three-way control valve（12.1）A mouths and the hydraulic control two-way valve（10）B control mouths, the drift hydraulic cylinder（15）Rodless cavity
Connection, the triple valve（13）A mouths and tee joint machine-hydraulic servo（12）Valve element driving hydraulic cylinder（12.3）Rodless cavity connect
It is logical, the low pressure constant displacement pump（1）Oil inlet, the high pressure constant displacement pump（2）Oil inlet, the low pressure sequences valve（4）Go out
Hydraulic fluid port, the three-way control valve（12.1）T mouths, the triple valve（13）T mouths connected with hydraulic oil container.
A kind of 2. hydraulic system of high speed drift according to claim 1, it is characterised in that：The tee joint machine-liquid servo
Valve（12）Mainly include three-way control valve（12.1）, position feedback loop（12.2）, valve element driving hydraulic cylinder（12.3）, threeway control
Valve（12.1）Valve element and valve element driving hydraulic cylinder（12.3）Piston rod be connected as an entirety, position feedback loop（12.2）Peace
Loaded on valve element driving hydraulic cylinder（12.3）Piston rod on, position feedback loop（12.2）In valve element driving hydraulic cylinder（12.3）Piston
Position adjustments on bar.
A kind of 3. hydraulic system of high speed drift according to claim 1, it is characterised in that：The triple valve（13）Valve
The big I consecutive variations of mouth, the triple valve（13）Valve element commutating period can adjust, the triple valve（13）Valve element on have
One machine feedback push rod, the triple valve（13）Also there is reversing handle, possess manual reverse of direction function.
A kind of 4. hydraulic system of high speed drift according to claim 1,2,5, it is characterised in that：The drift hydraulic cylinder
（15）For driving drift, the drift hydraulic cylinder（15）Piston rod and the valve element driving hydraulic cylinder（12.3）Cylinder body lead to
Cross the connecting plate（14）It is connected as an entirety, the triple valve（13）It is fixedly installed in the valve element driving hydraulic cylinder
（12.3）Cylinder body, the drift hydraulic cylinder（15）Piston rod, the triple valve（13）, the valve element driving hydraulic cylinder
（12.3）Cylinder body three move together, the triple valve（13）The contact of machine feedback push rod or depart from the position feedback loop
（12.2）.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711202856.7A CN107842530B (en) | 2017-11-27 | 2017-11-27 | A kind of hydraulic system of high speed formed punch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711202856.7A CN107842530B (en) | 2017-11-27 | 2017-11-27 | A kind of hydraulic system of high speed formed punch |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107842530A true CN107842530A (en) | 2018-03-27 |
| CN107842530B CN107842530B (en) | 2019-05-31 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711202856.7A Active CN107842530B (en) | 2017-11-27 | 2017-11-27 | A kind of hydraulic system of high speed formed punch |
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| CN (1) | CN107842530B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114951628A (en) * | 2021-02-24 | 2022-08-30 | 宝山钢铁股份有限公司 | Continuous casting submersed nozzle clamping system and method |
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| CN101121303A (en) * | 2007-08-10 | 2008-02-13 | 广东工业大学 | Hydraulic press punching active damping control device |
| CN101451550A (en) * | 2007-12-04 | 2009-06-10 | 中南大学 | Hydraulic synchronous driving system based on pressure feedback |
| CN201173221Y (en) * | 2008-02-29 | 2008-12-31 | 中国船舶重工集团公司第七一三研究所 | Electrohydraulic servo system power-off protection device |
| CN202097266U (en) * | 2011-05-04 | 2012-01-04 | 济南铸造锻压机械研究所有限公司 | Electric hydraulic control device of numerical control flat punching machine |
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| CN102588393A (en) * | 2012-03-12 | 2012-07-18 | 山东法因数控机械股份有限公司 | High-speed punching hydraulic circuit of hydraulic punching machine |
| CN202468560U (en) * | 2012-03-12 | 2012-10-03 | 山东法因数控机械股份有限公司 | High-speed punching hydraulic loop of hydraulic punching machine |
| CN203879827U (en) * | 2014-05-28 | 2014-10-15 | 吴汀 | Servo drive hydraulic system |
| CN104791310A (en) * | 2015-02-06 | 2015-07-22 | 湘潭大学 | Flow recycling energy-saving type segment erector horizontal movement hydraulic control system |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114951628A (en) * | 2021-02-24 | 2022-08-30 | 宝山钢铁股份有限公司 | Continuous casting submersed nozzle clamping system and method |
| CN114951628B (en) * | 2021-02-24 | 2024-04-05 | 宝山钢铁股份有限公司 | Continuous casting immersion nozzle clamping system and method |
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