CN107504020B - A kind of isothermal die forging process hydraulic system of press - Google Patents
A kind of isothermal die forging process hydraulic system of press Download PDFInfo
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- CN107504020B CN107504020B CN201710958167.2A CN201710958167A CN107504020B CN 107504020 B CN107504020 B CN 107504020B CN 201710958167 A CN201710958167 A CN 201710958167A CN 107504020 B CN107504020 B CN 107504020B
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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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- 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
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
-
- 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
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
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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
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Control Of Presses (AREA)
- Forging (AREA)
Abstract
The invention belongs to isothermal die forging process technical field of pressing machine, and in particular to a kind of isothermal die forging process hydraulic system of press.The first plunger case of sliding block upper center is connected to including working end, piston rod is connected to the first piston cylinder and second piston cylinder at both ends above sliding block, No.1 piston cylinder driving circuit, No. two piston cylinder driving circuits, No. three plunger case circuits, die forging circuit, relief circuit, sliding block backhaul circuit.The operating pressure of hydraulic system realizes stepless quick change by the use of proportional pressure control valve；The operating pressure output that three kinds of different gradients may be implemented by the combination of hydraulic cylinder different operating mode, realizes on-demand output；The demand that the different operating conditions of the small flow of low speed heavy pressure and high velocity, low pressure big flow are met by the Collaborative Control of proportioning pump and high frequency sound proportional servo valve realizes the grading control and output on demand of flow, controls more intelligent.
Description
Technical field
The invention belongs to isothermal die forging process technical field of pressing machine, and in particular to a kind of isothermal die forging process hydraulic system of press.
Background technique
Isothermal die forging process press is one of the important equipment for forging large-scale precision monoblock type forging part.Due to titanium alloy, high temperature
Narrow forging temperature, the resistance of deformation of the large-scale precisions forging part such as alloy are big, rate of deformation requires stringent, conventional die forging pressure
Machine can no longer meet the requirement of forging technology.Isothermal die forging process press, which refers to, is heated to temperature identical with workpiece for mold, permanent
Pressure maintaining for a period of time, a kind of advanced forging forming equipment of forging process is completed with extremely low rate of deformation, it is desirable that sliding block after temperature
Die forging 0.5 ~ 10mm/s of speed controllable adjustment, isothermal forging speed 0.005 ~ 0.5mm/s controllable adjustment.
The isothermal die forging process press hydraulic control system designed both at home and abroad at present, as shown in Figure 1: when sliding block fast downlink,
Electromagnet Y2, Y4, Y6 obtain electric, and three-position four-way electromagnetic directional valve C1, C2, C3 work in right position, at the same electromagnet Y7 obtain it is electric, two
Position three-way solenoid valve D work is in right position, and proportion electro-magnet YB1, YB2, YB3 obtain electric, and proportional flow control valve E1, E2, E3 start
Work, at the same electromagnet Y10, Y11 obtain it is electric.Hydraulic oil is come out by pumping source A1, A2, A3, by three-position four-way electromagnetic directional valve C1,
C2, C3, proportional flow control valve E1, E2, E3 are separately flowed into plunger case I1, I2, I3, and sliding block is during downlink, top petrol tank
The hydraulic oil of 13 the insides flows in corresponding plunger case respectively by check valve H1, H2, H3, and sliding block obtains maximum downlink
Driving speed, when upper mold touches workpiece, electromagnet Y11 power-off, electromagnet Y12 obtain it is electric, system start generate back pressure, into
Enter the reduction of master cylinder flow, sliding block slow running.When system enters the isothermal forging stage, oil circuit is switched to driven at low speed, oil liquid
Individually by pumping source A3, column is flowed by three-position four-way electromagnetic directional valve C3, two-bit triplet solenoid directional control valve Q and proportional servo valve F
In plug cylinder I1, I2, I3, collaborate to realize driven at low speed by multi-cylinder.The hydraulic system cannot realize the position of sliding block quasi-
Really control；When low speed is run, control inaccuracy is realized to three hydraulic cylinders by a proportional servo valve, due to three pipes
The error of different in size and three hydraulic cylinders on road in process is likely to result in partially during slide block down
It carries, to cause the pressure fluctuation and impact of pipeline；It is dynamic to provide that the backhaul of sliding block needs separately to set individual kicker cylinder J1 and J2
Power, configuring redundancy.
Summary of the invention
It, can be efficiently against existing skill the purpose of the present invention is providing a kind of novel hydraulic system for isothermal die forging process press
Art there are the shortcomings that.
The present invention is achieved by the following technical solutions: a kind of isothermal die forging process hydraulic system of press, including working end connects
It is connected to the first plunger case of sliding block upper center, piston rod is connected to the first piston cylinder at both ends and second above sliding block and lives
Plug cylinder, No.1 piston cylinder driving circuit, No. two piston cylinder driving circuits, No. three plunger case circuits, die forging circuit, relief circuit,
Sliding block backhaul circuit,
It is respectively equipped with built in magnetic hysteresis telescopic displacement sensor and second built in first in first piston cylinder and second piston cylinder
Magnetic hysteresis telescopic displacement sensor；
No.1 piston cylinder driving circuit includes the first pressure reducing valve that oil inlet is attached on principal pressure oil pipe, is attached to first
First liang of position and four-way reversing valve on pressure reducing valve oil outlet, the first superposition being attached on first liang of position and four-way reversing valve oil outlet
Throttle grverning valve, the first quick liquid filling valve being attached on the first superposition throttle grverning valve, the oil outlet of the first quick liquid filling valve
It is connected with the rodless cavity of first piston cylinder, the oil inlet of the first quick liquid filling valve couples with top petrol tank；
Similarly No. two piston cylinder driving circuits and No. three plunger case circuits, and the third in No. three plunger case circuits is fast
The oil outlet of fast prefill valve and the upper working chamber of the first plunger case are connected；
Piston cylinder oil return circuit includes the 8 on the B mouthfuls of rod chambers for being respectively coupled to first piston cylinder and second piston cylinder
Inserted valve of the cover board with shuttle valve, oil inlet are attached to the 4th band pressure difference compensation on the A mouth of the 8th inserted valve of the cover board with shuttle valve
High frequency sound proportional servo valve, the oil return opening of the 4th high frequency sound proportional servo valve with pressure difference compensation is attached to by main oil return pipe
Fuel tank；
Die forging circuit include the shaft orientation plunger variable pump being parallel between fuel tank and principal pressure oil pipe, big flow proportioning pump,
Small flow proportional pump, control oil pump, oil inlet are respectively coupled to inserted valve of first cover board with shuttle valve on principal pressure oil pipe, the
Inserted valve of two cover boards with shuttle valve, inserted valve of the third cover board with shuttle valve, oil inlet are respectively coupled to the first cover board with shuttle valve
The high frequency of the inserted valve of inserted valve, the second cover board with shuttle valve, first band pressure difference compensation on inserted valve of the third cover board with shuttle valve
Ring proportional servo valve, the second high frequency sound proportional servo valve with pressure difference compensation, high frequency sound proportional servo of the third with pressure difference compensation
Valve, A mouthfuls are respectively coupled to the high frequency sound ratio of the high frequency sound proportional servo valve of first band pressure difference compensation, second with pressure difference compensation and watch
Take the 5th inserted valve of the cover board with shuttle valve, the 6th cover board band shuttle on the high frequency sound proportional servo valve of valve, third with pressure difference compensation
The inserted valve of valve, the 7th inserted valve of the cover board with shuttle valve, inserted valve of the 5th cover board with shuttle valve, the 6th cover board are with shuttle valve
Inserted valve, the 7th inserted valve of the cover board with shuttle valve B mouth be respectively coupled to the rod chamber of first piston cylinder, second piston cylinder has
The upper working chamber of rod cavity and the first plunger case；
Relief circuit include inlet respectively with the rodless cavity of first piston cylinder, the rodless cavity of second piston cylinder and first
The joining fast draining valve of upper working chamber of plunger case, the fast draining valve oil return opening couple with main oil return pipe；
Sliding block backhaul circuit includes No.1 piston cylinder driving circuit, No. two piston cylinder driving circuits, No. three plunger case circuits
And piston cylinder oil return circuit, and the A mouth of the 4th inserted valve of the cover board with shuttle valve is connected with principal pressure oil pipe, top petrol tank is logical
It crosses drain mast and is attached to fuel tank.
Advantage of the present invention and good effect are:
1, stepless control may be implemented in the downlink and opening speed of isothermal die forging process press slide, improves isothermal die forging process press
Stability of the hydraulic system under low-speed heave-load.
2, the operating pressure of hydraulic system realizes stepless quick change by the use of proportional pressure control valve；Pass through hydraulic cylinder
The operating pressure output of three kinds of different gradients may be implemented in the combination of different operating mode, realizes on-demand output；Pass through ratio
The Collaborative Control of pump and high frequency sound proportional servo valve meets the different operating conditions of the small flow of low speed heavy pressure and high velocity, low pressure big flow
Demand, realize flow grading control and on demand output, control it is more intelligent.
3, electric current is obtained by controlling the proportion electro-magnet of fast draining valve, the steady of high pressure in operating cylinder may be implemented
Release, avoid operating cylinder release high pressure when compression shock generation.
Detailed description of the invention
In order to more clearly explain the embodiment of the invention or the technical proposal in the existing technology, to embodiment or will show below
There is attached drawing needed in technical description to be briefly described, it should be apparent that, the accompanying drawings in the following description is only this
Some embodiments of invention for those of ordinary skill in the art without creative efforts, can be with
It obtains other drawings based on these drawings.
Fig. 1 is prior art isothermal die forging process hydraulic system of press figure.
Fig. 2 is present hydraulic system pumping plant schematic diagram.
Fig. 3 is present hydraulic system control valve group schematic diagram.
Fig. 4 is isothermal forging process flow chart.
In figure: A1, A2, A3- pumping source, C1, C2, C3- three-position four-way electromagnetic directional valve, Y1, Y2, Y3, Y4, Y5, Y6, Y7,
Y9, Y10, Y11, Y12-electromagnet, D- two-bit triplet solenoid directional control valve, YB1, YB2, YB3- proportion electro-magnet, E1, E2, E3-
Proportional flow control valve, F- proportional servo valve, G- fuel tank, H1, H2, H3- check valve, I1, I2, I3- plunger case, J1, J2- kicker cylinder,
Q- two-bit triplet solenoid directional control valve, 1- shaft orientation plunger variable pump, 2.1- big flow proportioning pump, the small flow proportional pump of 2.2-, 3- control
Liquefaction pump, the first high pressure filter of 4.1-, the second high pressure filter of 4.2-, 4.3- third high pressure filter, the 4th high pressure of 4.4-
Filter, 5- proportional pressure control valve, the first check valve of 6.1-, 6.2- second one-way valve, 6.3- third check valve, 6.4- the 4th are unidirectional
Valve, inserted valve of the first cover board of 7.1- with shuttle valve, inserted valve of the second cover board of 7.2- with shuttle valve, 7.3- third cover board is with shuttle valve
Inserted valve, the 4th inserted valve of the cover board with shuttle valve of 7.4-, the high frequency sound proportional servo valve of 8.1- first band pressure difference compensation, 8.2-
The two high frequency sound proportional servo valves with pressure difference compensation, high frequency sound proportional servo valve of the 8.3- third with pressure difference compensation, 8.4- the 4th
High frequency sound proportional servo valve with pressure difference compensation, the 5th inserted valve of the cover board with shuttle valve of 9.1-, the 6th cover board of 9.2- is with shuttle valve
Inserted valve, the 7th inserted valve of the cover board with shuttle valve of 9.3-, the 8th inserted valve of the cover board with shuttle valve of 9.4-, the first pressure reducing valve of 10.1-,
The second pressure reducing valve of 10.2-, 10.3- third pressure reducing valve, first liang of position and four-way reversing valve of 11.1-, the second two four-way commutations of 11.2-
Valve, two position and four-way reversing valve of 11.3- third, 12.1- first are superimposed throttle grverning valve, and 12.2- second is superimposed throttle grverning valve,
12.3- third is superimposed throttle grverning valve, 13- top petrol tank, the first ball relief valve of 14.1-, the second ball relief valve of 14.2-, 14.3-
Third ball relief valve, the first quick liquid filling valve of 15.1-, the second quick liquid filling valve of 15.2-, 15.3- third quick liquid filling valve,
Magnetic hysteresis telescopic displacement sensor built in 16.1- first, magnetic hysteresis telescopic displacement sensor built in 16.2- second, the first plunger of 17-
Cylinder, 18.1- first piston cylinder, 18.2- second piston cylinder, 19- fast draining valve, P- principal pressure oil pipe, the main oil return pipe of T-, X- control
Liquefaction pipe, L- drain mast.
Specific embodiment
To make the object, technical solutions and advantages of the present invention clearer, technical solution of the present invention will be carried out below
Detailed description.Obviously, described embodiments are only a part of the embodiments of the present invention, instead of all the embodiments.Base
Embodiment in the present invention, those of ordinary skill in the art are obtained all without making creative work
Other embodiment belongs to the range that the present invention is protected.
Technical solution of the present invention is described in detail with reference to the accompanying drawing.
A kind of isothermal die forging process hydraulic system of press is connected to the first plunger case 17 of sliding block upper center including working end,
Piston rod is connected to the first piston cylinder 18.1 and second piston cylinder 18.2 at both ends above sliding block, and No.1 piston cylinder drives back
Road, No. two piston cylinder driving circuits, No. three plunger case circuits, die forging circuit, relief circuit, sliding block backhaul circuit,
Magnetic hysteresis telescopic displacement sensor built in first is respectively equipped in first piston cylinder 18.1 and second piston cylinder 18.2
Magnetic hysteresis telescopic displacement sensor 16.2 built in 16.1 and second；
No.1 piston cylinder driving circuit includes the first pressure reducing valve 10.1 that oil inlet is attached on principal pressure oil pipe P, connection
First liang of position and four-way reversing valve 11.1 on to 10.1 oil outlet of the first pressure reducing valve, is attached to first liang of position and four-way reversing valve 11.1
The first superposition throttle grverning valve 12.1 on oil outlet, the first quick filling liquid being attached on the first superposition throttle grverning valve 12.1
The rodless cavity of valve 15.1, the liquid outlet and first piston cylinder 18.1 of the first quick liquid filling valve 15.1 is connected, the first quick filling liquid
The inlet of valve 15.1 couples with top petrol tank 13；
Similarly No. two piston cylinder driving circuits and No. three plunger case circuits, and the third in No. three plunger case circuits is fast
The liquid outlet of fast prefill valve 15.3 and the upper working chamber of the first plunger case 17 are connected；
Piston cylinder oil return circuit includes the B mouthfuls of rod chambers for being respectively coupled to first piston cylinder 18.1 and second piston cylinder 18.2
On inserted valve 9.4 of the 8th cover board with shuttle valve, oil inlet is attached on the A mouth of inserted valve 9.4 of the 8th cover board with shuttle valve
The 4th high frequency sound proportional servo valve 8.4 with pressure difference compensation, the oil return of the 4th high frequency sound proportional servo valve 8.4 with pressure difference compensation
Mouth is attached to fuel tank G by main oil return pipe T；
Die forging circuit includes the shaft orientation plunger variable pump 1 being parallel between fuel tank G and principal pressure oil pipe P, big flow ratio
Pump 2.1, small flow proportional pump 2.2, control oil pump 3, and oil inlet is respectively coupled to the band shuttle valve of the first cover board on principal pressure oil pipe P
The inserted valve 7.2 of inserted valve 7.1, the second cover board with shuttle valve, inserted valve 7.3 of the third cover board with shuttle valve, oil inlet joins respectively
It is connected to the inserting of inserted valve 7.2, third cover board with shuttle valve of inserted valve 7.1 of first cover board with shuttle valve, the second cover board with shuttle valve
High frequency sound proportional servo of the high frequency sound proportional servo valve 8.1, second with pressure difference compensation of first band pressure difference compensation on valve 7. 3
The high frequency sound proportional servo valve 8.3 of valve 8.2, third with pressure difference compensation, the A mouthfuls of high frequency sounds for being respectively coupled to first band pressure difference compensation
High frequency sound proportional servo valve 8.2 of the proportional servo valve 8.1, second with pressure difference compensation, high frequency sound ratio of the third with pressure difference compensation
Inserted valve 9.1, sixth cover board inserted valve 9.2 with shuttle valve of the 5th cover board with shuttle valve, the 7th cover board band shuttle on servo valve 8.3
The inserted valve 9.3 of valve, the inserted valve the 9.2, the 7th of the inserted valve 9.1 of the 5th cover board with shuttle valve, the 6th cover board with shuttle valve cover
The B mouth of the inserted valve 9.3 of strip shuttle valve is respectively coupled to the rod chamber of first piston cylinder 18.1, second piston cylinder 18.2 has bar
The upper working chamber of chamber and the first plunger case 17；
Relief circuit includes rodless cavity of the inlet respectively with the rodless cavity of first piston cylinder 18.1, second piston cylinder 18.2
And first plunger case 17 the joining fast draining valve 19 of upper working chamber, 19 oil return opening of fast draining valve and main oil return
Pipe T connection；
Sliding block backhaul circuit includes No.1 piston cylinder driving circuit, No. two piston cylinder driving circuits, No. three plunger case circuits
And piston cylinder oil return circuit, and the A mouth of inserted valve 7.4 of the 4th cover board with shuttle valve is connected with principal pressure oil pipe P, high-order oil
Case 13 is attached to fuel tank G by drain mast L.
Specifically, No.1 piston cylinder driving circuit is as shown in Fig. 2, the first pressure reducing valve 10.1 and the first two four-way commutations
The oil return opening of valve 11.1 couples with main oil return pipe T.The oil return opening of the high frequency sound proportional servo valve 8.1 of first band pressure difference compensation passes through
Check valve couples with main oil return pipe T；The control port of the high frequency sound proportional servo valve 8.1 of first band pressure difference compensation and control oil pipe
X connection, unloading port couple with drain mast L；The drain tap of inserted valve 9.1 of 5th cover board with shuttle valve couples with drain mast L.First
10.1, first liang of position and four-way reversing valves 11.1 of pressure reducing valve and the first superposition throttle grverning valve 12.1 are superimposed, the first lid
Together with the inserted valve 7.1 of strip shuttle valve can integrate with the high frequency sound proportional servo valve 8.1 of first band pressure difference compensation, and first
10.1, first liang of position and four-way reversing valves 11.1, first of pressure reducing valve are superimposed the inserting of throttle grverning valve 12.1, the first cover board with shuttle valve
Valve 7.1, first band pressure difference compensation the inserted valve 9.1 of high frequency sound proportional servo valve 8.1 and the 5th cover board with shuttle valve can pass through valve
The inner duct of block is coupled to each other.Similarly No. two piston cylinder driving circuits and No. three plunger case circuits.
Further, relief circuit is as shown in Fig. 2, the control port of fast draining valve 19 couples with control oil pipe X, quickly
The 7.4, the 4th high frequency sound proportional servo valve 8.4 and the 8th with pressure difference compensation of inserted valve of tapping valve 19 and the 4th cover board with shuttle valve
Inserted valve 9.4 of the cover board with shuttle valve can be coupled to each other by the inner duct of valve block.
As shown in Fig. 2, the unloading port of inserted valve of each cover board with shuttle valve couples with drain mast L.
Preferably, be sequentially connected in series between shaft orientation plunger variable pump 1 and principal pressure oil pipe P the first high pressure filter 4.1 and
First check valve 6.1.Similarly the second high-pressure filteration has been sequentially connected in series between the big flow proportioning pump 2.1 and principal pressure oil pipe P
Device 4.2 and second one-way valve 6.2, small flow proportional pump and have been sequentially connected in series third high pressure filter between 2.2 and principal pressure oil pipe P
4.3 and third check valve 6.3.And control oil pump 3 is also in series between fuel tank G and principal pressure oil pipe P, control oil pump 3 and main pressure
The 4th high pressure filter 4.4 and the 4th check valve 6.4 have been sequentially connected in series between power oil pipe P.
Further, first quick liquid filling valve 15.1, the second quick liquid filling valve 15.2, third quick liquid filling valve 15.3
It is in series with the first ball relief valve 14.1, the second ball relief valve 14.2, third ball relief valve 14.3 respectively between top petrol tank 13.
As shown in Figures 2 and 3, the guarantee of drop press slide position precision mainly passes through the flexible position of magnetic hysteresis built in first
Magnetic hysteresis telescopic displacement sensor the second high frequency of 16.2+ built in the first high frequency sound of displacement sensor 16.1+ proportional servo valve 8.1 and second
Proportional servo valve 8.2 is rung to respectively constitute position closed loop and realize accurate control；The grading control of flow mainly passes through big flow
Proportioning pump 2.1, small flow proportional pump 1 parallel drive of 2.2+ shaft orientation plunger variable pump and the high frequency sound with first band pressure difference compensation
High frequency sound proportional servo valve 8.2 of the proportional servo valve 8.1, second with pressure difference compensation, high frequency sound ratio of the third with pressure difference compensation
8.3 Collaborative Control of servo valve meets the requirements of two kinds of operating conditions of the small flow of low speed heavy pressure and high velocity, low pressure big flow, ensure that
The low-speed stable of warm die forging machine is run；The stepless change of main system pressure is realized by proportional pressure control valve 5.During forging and stamping,
Slide block down velocity interval is 0.005mm/s -10mm/s, and rate request range is bigger, and maximum speed is compared with minimum speed
Compared with, numerically be difference 2000 times；Moreover, the flow control of proportional servo valve is in opening degree maximum and opening degree minimum, it is defeated
The linear relationship for entering electric current and output flow is unobvious, is difficult to by single proportional servo valve to carry out control to ram speed
Reach actual demand.So the invention pumps high frequency of the 2.2+ with pressure difference compensation using big flow proportioning pump 2.1, small flow proportional
Proportional servo valve Collaborative Control is rung, to ensure that proportioning pump and proportional servo valve can works under the operating condition of high-pressure low-flow
Make in linear region.The backhaul of sliding block is realized by first piston cylinder 18.1, the 18.2 rod chamber oil inlet of second piston cylinder.First
The ratio between 17 work area of plunger case and first piston cylinder 18.1,18.2 work area of second piston cylinder are 2:1.
The process flow chart of isothermal die forging process is as shown in figure 4, specifically include that quick pressure, die forging, isothermal die forging process, pressure maintaining rank
Section, off-load, quick return, at a slow speed backhaul.
When sliding block fast downlink, the high pressure oil in principal pressure oil pipe P passes through the decompression of the first pressure reducing valve 10.1, second respectively
Valve 10.2, third pressure reducing valve 10.3, first liang of position and four-way reversing valve, 11.1, second liang of position and four-way reversing valves 11.2, third two
Four-way reversing valve 11.3, the first superposition throttle grverning valve 12.1, second is superimposed throttle grverning valve 12.2, third is superimposed throttle grverning
Valve 12.3 opens the first quick liquid filling valve 15.1, the second quick liquid filling valve 15.2, third quick liquid filling valve 15.3, top petrol tank
It is fast that 13 hydraulic oil passes through the first quick liquid filling valve 15.1, the second quick liquid filling valve 15.2, third quick liquid filling valve 15.3 respectively
Speed enters 18.1 rodless cavity of first piston cylinder, on 18.2 rodless cavity of second piston cylinder and the first plunger case 17 in working chamber, drives
Movable slider fast downlink, the speed that quick liquid filling valve is opened can pass through the first superposition superposition section of throttle grverning valve 12.1, second
Stream speed governing valve 12.2, third superposition throttle grverning valve 12.3 are adjusted respectively.18.1 rod chamber of first piston cylinder and the simultaneously
Hydraulic oil in two piston cylinders, 18.2 rod chamber passes through inserted valve 9.4 of the 8th cover board with shuttle valve, the 4th height with pressure difference compensation
The oil return opening of frequency response proportional servo valve 8.4 enters main oil return pipe T and then flows back to fuel tank G, and the speed of sliding block fast downlink can lead to
The proportion electro-magnet BY8 for crossing the 4th high frequency sound proportional servo valve 8.4 with pressure difference compensation of control obtains the size of electric current and is adjusted
Section, the size of high frequency sound proportional servo valve valve core opening degree are directly proportional to size of current.
When the setting value of sliding block fast downlink to displacement sensor, the first quick liquid filling valve 15.1, the second quick filling liquid
Valve 15.2, third quick liquid filling valve 15.3 are closed rapidly, shaft orientation plunger variable pump 1, big flow proportioning pump 2.1, small flow proportional
Pump 2.2 is rapidly by hydraulic oil by the first high pressure filter 4.1, the second high pressure filter 4.2, third high pressure filter 4.3, the
One check valve 6.1, second one-way valve 6.2, third check valve 6.3 be flowed into principal pressure oil pipe P, then principal pressure oil pipe P
High pressure oil passes through inserted valve 7.1 of first cover board with shuttle valve, inserted valve 7.2 of second cover board with shuttle valve, third cover board band respectively
The inserted valve 7.3 of shuttle valve, high frequency sound ratio of the high frequency sound proportional servo valve 8.1, second of first band pressure difference compensation with pressure difference compensation
The inserted valve 9.1 of high frequency sound proportional servo valve 8.3 and the 5th cover board with shuttle valve of example servo valve 8.2, third with pressure difference compensation,
Inserted valve 9.2, seventh cover board inserted valve 9.3 with shuttle valve of 6th cover board with shuttle valve, quickly enters 18.1 nothing of first piston cylinder
Driving sliding block continues traveling downwardly carry out die forging in working chamber on rod cavity, 18.2 rodless cavity of second piston cylinder and the first plunger case 17.Mould
The speed of forging is 0.5 ~ 10mm/s, can be electric by controlling the ratio of the high frequency sound proportional servo valve 8.1 of first band pressure difference compensation
The height of proportion electro-magnet BY3, third with pressure difference compensation of the high frequency sound proportional servo valve 8.2 of magnet B Y1, second with pressure difference compensation
The proportion electro-magnet BY5 of frequency response proportional servo valve 8.3 obtain the size of electric current to the oil liquid for entering each hydraulic cylinder number into
Row is individually adjusted, and the size of proportional servo valve valve core opening degree is directly proportional to size of current.In die forging process, magnetic hysteresis built in first
The high frequency sound with first band pressure difference compensation respectively of magnetic hysteresis telescopic displacement sensor 16.2 built in telescopic displacement sensor 16.1, second
High frequency sound proportional servo valve 8.2 of the proportional servo valve 8.1, second with pressure difference compensation forms position closed loop to the position precision of sliding block
Adjustment in real time is carried out to meet actual process requirement.In die forging process, using the output displacement of first piston cylinder 18.1 as reference
Value, the output displacement of second piston cylinder 18.2 and its when comparing generation deviation, data feedback that displacement sensor will test to
Control current signal is transmitted to each high frequency sound proportional servo valve, and then right after calculation process by industrial control computer respectively
The opening degree of each high frequency sound proportional servo is adjusted, to ensure that moving synchronously for three hydraulic cylinders, avoids unbalance loading
The generation of phenomenon.
When system carries out isothermal forging, isothermal forging 0.005 ~ 0.5mm/s of speed, flow needed for system is less, axial
1 off-load of plunger variable pump, in the 8.1, second high frequency sound with pressure difference compensation of high frequency sound proportional servo valve of first band pressure difference compensation
The high frequency sound ratio of proportional servo valve 8.2, third with the high frequency sound proportional servo valve 8.3 of pressure difference compensation and the 4th with pressure difference compensation
The example work of servo valve 8.4 is in the case where linear zone, by adjusting 2.2 control of big flow proportioning pump 2.1 and small flow proportional pump
The input size of voltage meets the needs of actual condition, ratio pump output flow number with the size of input control voltage at
Direct ratio only needs small 2.2 work of flow proportional pump when isothermal forging speed is 0.005 mm/s；When isothermal forging speed is 0.5
When mm/s, big flow proportioning pump 2.1 and small flow proportional pump 2.2 simultaneously participate in work；When isothermal forging speed is 0.005 mm/
When 0.5 section mm/s s-, two proportioning pumps can be worked at the same time, and can also be worked independently with a proportioning pump, according to practical work
Condition demand, flow are supplied on demand.First plunger case, 17 work area and first piston cylinder 18.1, second piston cylinder 18.2 are big
The ratio between chamber work area is 2:1, according to the difference of operating pressure needed for practical forging and stamping workpiece, can choose different combinations
Work: the first plunger case 17 works independently when slide block down, and first piston cylinder 18.1, second piston cylinder 18.2 are servo-actuated, only
It works in backhaul；First piston cylinder 18.1, second piston cylinder 18.2 work respectively when slide block down, the first plunger case 17 with
It is dynamic；The first plunger case 17, first piston cylinder 18.1, second piston cylinder 18.2 simultaneously participate in work when slide block down；Three kinds hydraulic
The operating pressure output of three kinds of different gradients may be implemented in the combination of cylinder different operating mode, and operating pressure realizes defeated on demand
Out, the waste of the energy is avoided.When system unloaded, the proportion electro-magnet BY9 of fast draining valve 19 obtain it is electric, the speed of off-load with
BY9 obtains that electric size of current is directly proportional, ensure that the steady release of high pressure oil in operating cylinder, when avoiding system release high pressure
Compression shock.
When sliding block backhaul, the high pressure oil of principal pressure oil pipe P passes through inserted valve 7.4 of the 4th cover board with shuttle valve, the
Four inserted valves 9.4 of high frequency sound proportional servo valve 8.4 and the 8th cover board with shuttle valve with pressure difference compensation, quickly enter first piston
Sliding block quick return is driven in 18.1 rod chamber of cylinder and 18.2 rod chamber of second piston cylinder, the speed of sliding block quick return can lead to
The proportion electro-magnet BY7 for crossing the 4th high frequency sound proportional servo valve 8.4 with pressure difference compensation of control obtains the size of electric current and is adjusted
Section, the size of high frequency sound proportional servo valve valve core opening degree are directly proportional to size of current.Meanwhile hydraulic oil passes through first respectively and subtracts
Pressure valve 10.1, the second pressure reducing valve 10.2, third pressure reducing valve 10.3, first liang of position and four-way reversing valve 11.1, the second two four-ways change
To valve 11.2, two position and four-way reversing valve 11.3 of third, the first superposition throttle grverning valve 12.1, second is superimposed throttle grverning valve
12.2, third is superimposed throttle grverning valve 12.3, and it is fast to open the first quick liquid filling valve 15.1, the second quick liquid filling valve 15.2, third
Fast prefill valve 15.3, working chamber on 18.1 rodless cavity of first piston cylinder, 18.2 rodless cavity of second piston cylinder and the first plunger case 17
Interior hydraulic oil passes through respective quick liquid filling valve respectively and flows back in top petrol tank 13, sliding block quick return.When sliding block quickly returns
Journey to displacement sensor position setting value when, the first quick liquid filling valve 15.1, the second quick liquid filling valve 15.2, third are quickly filled
Liquid valve 15.3 is closed rapidly, 18.2 nothing of working chamber, 18.1 rodless cavity of first piston cylinder and second piston cylinder on the first plunger case 17
Hydraulic oil in rod cavity passes through inserted valve 9.1 of the 5th cover board with shuttle valve, inserted valve 9.2 of the 6th cover board with shuttle valve, respectively
Inserted valve 9.3 of seven cover boards with shuttle valve, the high frequency sound proportional servo valve 8.1, second of first band pressure difference compensation is with pressure difference compensation
The oil return opening of the high frequency sound proportional servo valve 8.3 of high frequency sound proportional servo valve 8.2 and third with pressure difference compensation flows back to fuel tank respectively.
At a slow speed the speed of backhaul can by control first band pressure difference compensation high frequency sound proportional servo valve 8.1 proportion electro-magnet BY2,
The high frequency sound ratio of proportion electro-magnet BY4, third with pressure difference compensation of the second high frequency sound proportional servo valve 8.2 with pressure difference compensation
The size that the proportion electro-magnet BY6 of servo valve 8.3 obtains electric current flows back to how much carry out lists of the oil liquid of fuel tank to each oil circuit
It solely adjusts, the size of high frequency sound proportional servo valve valve core opening degree is directly proportional to size of current.Sliding block is at a slow speed during backhaul,
Magnetic hysteresis telescopic displacement sensor 16.2 built in magnetic hysteresis telescopic displacement sensor 16.1, first built in first respectively with first band pressure difference
High frequency sound proportional servo valve 8.2 of the high frequency sound proportional servo valve 8.1, second of compensation with pressure difference compensation forms position closed loop to cunning
The position precision of block is adjusted in real time, guarantees the synchronism of hydraulic cylinder in return stroke.When sliding block at a slow speed backhaul to limes superiors
When position, isothermal die forging process press stops working or is recycled next time.
The above description is merely a specific embodiment, but scope of protection of the present invention is not limited thereto, any
Those familiar with the art in the technical scope disclosed by the present invention, can easily think of the change or the replacement, and should all contain
Lid is within protection scope of the present invention.Therefore, protection scope of the present invention should be based on the protection scope of the described claims.
Claims (1)
1. a kind of isothermal die forging process hydraulic system of press, which is characterized in that including the first plunger case (17), first piston cylinder
(18.1), second piston cylinder (18.2), No.1 piston cylinder driving circuit, No. two piston cylinder driving circuits, No. three plunger case circuits,
Die forging circuit, relief circuit, sliding block backhaul circuit；
The working end of first plunger case (17) is connected to sliding block upper center, and the first piston cylinder (18.1) and second live
The piston rod of plug cylinder (18.2) is connected to both ends above sliding block, and first piston cylinder (18.1) and second piston cylinder (18.2) are interior
It is respectively equipped with magnetic hysteresis telescopic displacement sensor (16.1) built in first and magnetic hysteresis telescopic displacement sensor (16.2) built in second；
No.1 piston cylinder driving circuit includes the first pressure reducing valve (10.1), the be attached on the first pressure reducing valve (10.1) oil outlet
One liang of position and four-way reversing valve (11.1), the first superposition throttling being attached on first liang of position and four-way reversing valve (11.1) oil outlet are adjusted
Fast valve (12.1), the first quick liquid filling valve (15.1) being attached on the first superposition throttle grverning valve (12.1), first quickly fills
The liquid outlet of liquid valve (15.1) and the rodless cavity of first piston cylinder (18.1) are connected, the feed liquor of the first quick liquid filling valve (15.1)
Mouth couples with top petrol tank (13), and the oil inlet of the first pressure reducing valve (10.1) is attached on principal pressure oil pipe (P)；
No. two piston cylinder driving circuits include the second pressure reducing valve (10.2), the be attached on the second pressure reducing valve (10.2) oil outlet
Two liang of position and four-way reversing valves (11.2), the second superposition throttling being attached on second liang of position and four-way reversing valve (11.2) oil outlet are adjusted
Fast valve (12.2), the second quick liquid filling valve (15.2) being attached on the second superposition throttle grverning valve (12.2), second quickly fills
The liquid outlet of liquid valve (15.2) and the rodless cavity of second piston cylinder (18.2) are connected, the feed liquor of the second quick liquid filling valve (15.2)
Mouth couples with top petrol tank (13), and the oil inlet of the second pressure reducing valve (10.2) is attached on principal pressure oil pipe (P)；
No. three plunger case circuits include third pressure reducing valve (10.3), the third two being attached on third pressure reducing valve (10.3) oil outlet
Position and four-way reversing valve (11.3), the third superposition throttle grverning valve being attached on two position and four-way reversing valve of third (11.3) oil outlet
(12.3), the third quick liquid filling valve (15.3) being attached in third superposition throttle grverning valve (12.3), third quick liquid filling valve
(15.3) the upper working chamber of liquid outlet and the first plunger case (17) is connected, the inlet of third quick liquid filling valve (15.3) with
Top petrol tank (13) connection, the oil inlet of third pressure reducing valve (10.3) are attached on principal pressure oil pipe (P)；
Piston cylinder oil return circuit includes inserted valve (9.4) of the 8th cover board with shuttle valve, the 4th high frequency sound ratio with pressure difference compensation
The B mouth of servo valve (8.4), inserted valve (9.4) of the 8th cover board with shuttle valve is respectively coupled to first piston cylinder (18.1) and second
On the rod chamber of piston cylinder (18.2), the oil inlet of the 4th high frequency sound proportional servo valve (8.4) with pressure difference compensation is attached to
On the A mouth of inserted valve (9.4) of eight cover boards with shuttle valve, the oil return of the 4th high frequency sound proportional servo valve (8.4) with pressure difference compensation
Mouth is attached to fuel tank (G) by main oil return pipe (T)；
Die forging circuit includes shaft orientation plunger variable pump (1), the big flow ratio being parallel between fuel tank (G) and principal pressure oil pipe (P)
Example pump (2.1), small flow proportional pump (2.2), control oil pump (3), inserted valve (7.1) of first cover board with shuttle valve, the second cover board
Inserted valve (7.2) with shuttle valve, inserted valve (7. 3) of the third cover board with shuttle valve, the high frequency sound ratio of first band pressure difference compensation are watched
It takes valve (8.1), the second high frequency sound proportional servo valve (8.2) with pressure difference compensation, third is watched with the high frequency sound ratio of pressure difference compensation
It takes valve (8.3), inserted valve (9.1) of the 5th cover board with shuttle valve, inserted valve (9.2) of the 6th cover board with shuttle valve, the 7th cover board band
The inserted valve (9.3) of shuttle valve；Inserted valve (7.1) of first cover board with shuttle valve, inserted valve of second cover board with shuttle valve
(7.2), the oil inlet of inserted valve (7. 3) of the third cover board with shuttle valve is respectively coupled on principal pressure oil pipe (P), and first is with pressure
The high frequency sound proportional servo valve (8.1) of difference compensation, the second high frequency sound proportional servo valve (8.2) with pressure difference compensation, third are with pressure
The oil inlet of the high frequency sound proportional servo valve (8.3) of difference compensation is respectively coupled to inserted valve (7.1) of first cover board with shuttle valve, the
On inserted valve (7.2) of two cover boards with shuttle valve, inserted valve (7. 3) of the third cover board with shuttle valve, the 5th cover board is with shuttle valve
The A mouth difference of the inserted valve (9.3) of inserted valve (9.2), the 7th cover board with shuttle valve of inserted valve (9.1), the 6th cover board with shuttle valve
It is attached to high frequency sound proportional servo valve (8.1), the second high frequency sound proportional servo valve with pressure difference compensation of first band pressure difference compensation
(8.2), on high frequency sound proportional servo valve (8.3) of the third with pressure difference compensation, the inserted valve of the 5th cover board with shuttle valve
(9.1), the B mouth of inserted valve (9.2), seventh cover board inserted valve (9.3) with shuttle valve of the 6th cover board with shuttle valve is respectively coupled to
The upper work of the rod chamber of first piston cylinder (18.1), the rod chamber of second piston cylinder (18.2) and the first plunger case (17)
Chamber；
Relief circuit includes fast draining valve (19), the inlet of the fast draining valve (19) respectively with first piston cylinder
(18.1) the rodless cavity of rodless cavity, second piston cylinder (18.2) and the upper working chamber of the first plunger case (17) is connected, institute
Fast draining valve (19) oil return opening is stated to couple with main oil return pipe (T)；
Sliding block backhaul circuit includes No.1 piston cylinder driving circuit, No. two piston cylinder driving circuits, No. three plunger case circuits and
Piston cylinder oil return circuit, and the A mouth of inserted valve (7.4) of the 4th cover board with shuttle valve is connected with principal pressure oil pipe (P), high-order oil
Case (13) is attached to fuel tank (G) by drain mast (L).
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| CN109751289B (en) * | 2019-01-21 | 2020-07-03 | 太原理工大学 | Hydraulic system of hydraulic hybrid radial forging machine |
| CN114321107B (en) * | 2021-11-12 | 2023-08-18 | 武汉船用机械有限责任公司 | Hydraulic control driving system |
| CN114165487B (en) * | 2021-12-16 | 2024-01-30 | 合肥合锻智能制造股份有限公司 | Hydraulic control system of composite material |
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| 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 |
| CN103537599B (en) * | 2013-10-18 | 2015-11-18 | 中南大学 | For control method and the control system thereof of forging press |
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Inventor after: Wang Tao Inventor after: He Dongping Inventor after: Huang Qingxue Inventor after: Wang Jun Inventor after: Gao Xiangyu Inventor after: Wang Yuelin Inventor after: Li Sha Inventor before: He Dongping Inventor before: Huang Qingxue Inventor before: Wang Tao Inventor before: Wang Jun Inventor before: Gao Xiangyu Inventor before: Wang Yuelin Inventor before: Li Sha |
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Application publication date: 20171222 Assignee: Nantong Dawei Machine Tool Co., Ltd. Assignor: Taiyuan University of Technology Contract record no.: 2019140000002 Denomination of invention: Isothermal die forging press hydraulic system Granted publication date: 20190226 License type: Exclusive License Record date: 20190725 |