CN107504020A - 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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- CN107504020A CN107504020A CN201710958167.2A CN201710958167A CN107504020A CN 107504020 A CN107504020 A CN 107504020A CN 201710958167 A CN201710958167 A CN 201710958167A CN 107504020 A CN107504020 A CN 107504020A
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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
-
- 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 loops, die forging loop, relief circuit, sliding block backhaul loop.The use of the operating pressure passing ratio overflow valve of hydraulic system realizes stepless quick change；The operating pressure that can realize three kinds of different gradients by the combination of hydraulic cylinder different operating mode exports, and realizes and exports on demand；The Collaborative Control of passing ratio pump and high frequency sound proportional servo valve meets the demand of the different operating modes of low speed heavy pressure low discharge and high velocity, low pressure big flow, realizes the grading control of flow and exports on demand, and control is 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 technology
Isothermal die forging process press is one of visual plant for forging large-scale precision monoblock type forging part.Due to titanium alloy, high temperature
The die forging pressure that the narrow forging temperature of the large-scale precision forging part such as alloy, resistance of deformation are big, rate of deformation requirement is strict, conventional
Machine can not meet the requirement of forging technology.Isothermal die forging process press refers to mould being heated to and workpiece identical temperature, perseverance
Pressurize 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 to sliding block after temperature
Die forging 0.5 ~ 10mm/s of speed controllable adjustments, isothermal forging speed 0.005 ~ 0.5mm/s controllable adjustments.
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 are operated in right position, at the same electromagnet Y7 obtain it is electric, two
Position three-way solenoid valve D is operated 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 descending, top petrol tank
The hydraulic oil of 13 the insides flows in each self-corresponding plunger case respectively by check valve H1, H2, H3, and sliding block obtains the descending of maximum
Actuating speed, when mold touches workpiece, electromagnet Y11 power-off, electromagnet Y12 obtain it is electric, system start produce back pressure, enter
Enter the reduction of master cylinder flow, sliding block slow running.When system enters the isothermal forging stage, oil circuit switches to driven at low speed, fluid
Individually by pumping source A3, post is flowed into 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, collaborated by multi-cylinder so as to realize driven at low speed.The hydraulic system can not be realized accurate to the position of sliding block
Really control；When low speed is run, control is inaccurate to be 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, it is likely to result in during slide block down partially
Carry, so as to cause the pressure fluctuation of pipeline and impact；The backhaul of sliding block needs separately to set single kicker cylinder J1 and J2 dynamic to provide
Power, configuring redundancy.
The content of the invention
The purpose of the present invention is to provide a kind of novel hydraulic system for isothermal die forging process press, can be efficiently against existing skill
The shortcomings that art is present.
The present invention is achieved by the following technical solutions：A kind of isothermal die forging process hydraulic system of press, including working end connect
The first plunger case of sliding block upper center is connected to, piston rod is connected to the first piston cylinder at both ends and second above sliding block and lived
Plug cylinder, No.1 piston cylinder driving circuit, No. two piston cylinder driving circuits, No. three plunger case loops, die forging loop, relief circuit,
Sliding block backhaul loop,
Magnetic hysteresis built in magnetic hysteresis telescopic displacement sensor and second built in first is respectively equipped with first piston cylinder and second piston cylinder
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 the first decompression
First liang of position and four-way reversing valve on valve oil-out, the first superposition throttling being attached on first liang of position and four-way reversing valve oil-out
Flow speed control valve, the first quick liquid filling valve being attached on the first superposition throttle grverning valve, the oil-out of the first quick liquid filling valve and
The rodless cavity of one piston cylinder is connected, and 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 loops, and the 3rd of No. three plunger case loops quickly fills
The upper working chamber of the oil-out of liquid valve and the first plunger case is connected；
Piston cylinder oil return circuit includes the 8th cover plate that B mouths are respectively coupled on the rod chamber of first piston cylinder and second piston cylinder
Inserted valve with shuttle valve, oil inlet are attached to the 4th height with pressure difference compensation on the A mouths of the 8th inserted valve of the cover plate with shuttle valve
Frequency response proportional servo valve, the oil return opening of the 4th high frequency sound proportional servo valve with pressure difference compensation are attached to oil by main oil return pipe
Case；
Die forging loop includes shaft orientation plunger variable pump, big flow proportioning pump, the rill being parallel between fuel tank and principal pressure oil pipe
Proportioning pump, control oil pump are measured, oil inlet is respectively coupled to inserted valve of first cover plate with shuttle valve, the second lid on principal pressure oil pipe
The inserted valve of strip shuttle valve, the 3rd inserted valve of the cover plate with shuttle valve, oil inlet are respectively coupled to inserting of first cover plate with shuttle valve
The high frequency sound ratio of the inserted valve of valve, the second cover plate with shuttle valve, first band pressure difference compensation on the 3rd inserted valve of the cover plate with shuttle valve
Example servo valve, the second high frequency sound proportional servo valve with pressure difference compensation, the 3rd high frequency sound proportional servo valve with pressure difference compensation, A
Mouth is respectively coupled to high frequency sound proportional servo valve, the second high frequency sound proportional servo with pressure difference compensation of first band pressure difference compensation
The 5th inserted valve of the cover plate with shuttle valve, the 6th cover plate band shuttle valve on the high frequency sound proportional servo valve of valve, the 3rd with pressure difference compensation
Inserted valve, the 7th inserted valve of the cover plate with shuttle valve, inserted valve of the 5th cover plate with shuttle valve, the 6th cover plate with shuttle valve insert
Dress valve, the B mouths of the 7th inserted valve of the cover plate with shuttle valve are respectively coupled to the rod chamber of first piston cylinder, second piston cylinder has bar
The upper working chamber of chamber and the first plunger case；
Relief circuit includes the inlet rodless cavity with first piston cylinder, the rodless cavity of second piston cylinder and the first plunger respectively
The joining fast draining valve of upper working chamber of cylinder, the fast draining valve oil return opening couple with main oil return pipe；
Sliding block backhaul loop includes No.1 piston cylinder driving circuit, No. two piston cylinder driving circuits, No. three plunger case loops and
Piston cylinder oil return circuit, and the A mouths of the 4th inserted valve of the cover plate with shuttle valve are connected with principal pressure oil pipe, top petrol tank is by letting out
Oil pipe is attached to fuel tank.
Advantage of the present invention and good effect are：
1st, the descending and opening speed of isothermal die forging process press slide can realize stepless control, improve isothermal die forging process press hydraulic pressure
Stability of the system under low-speed heave-load.
2nd, the use of the operating pressure passing ratio overflow valve of hydraulic system realizes stepless quick change；Pass through hydraulic cylinder
The combination of different operating mode can realize the operating pressure output of three kinds of different gradients, realize and export on demand；Passing ratio
The Collaborative Control of pump and high frequency sound proportional servo valve meets the different operating modes of low speed heavy pressure low discharge and high velocity, low pressure big flow
Demand, realize the grading control of flow and export on demand, control it is more intelligent.
3rd, by controlling the proportion electro-magnet of fast draining valve to obtain electric current, it is possible to achieve operating cylinder inner high voltage it is steady
Release, avoid operating cylinder release high pressure when compression shock generation.
Brief description of the drawings
In order to illustrate more clearly about the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing
There is the required accompanying drawing used in technology description to be briefly described, it should be apparent that, drawings in the following description are only this
Some embodiments of invention, for those of ordinary skill in the art, on the premise of not paying creative work, can be with
Other accompanying drawings are obtained according to these accompanying 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 valves, YB1, YB2, YB3- proportion electro-magnet, E1, E2, E3-
Proportional flow control valve, F- proportional servo valves, G- fuel tanks, H1, H2, H3- check valve, I1, I2, I3- plunger case, J1, J2- kicker cylinder,
Q- two-bit triplet solenoid directional control valves, 1- shaft orientation plunger variable pumps, 2.1- big flow proportioning pumps, 2.2- low discharge proportioning pumps, 3- controls
Liquefaction pump, the high pressure filters of 4.1- first, the high pressure filters of 4.2- second, the high pressure filters of 4.3- the 3rd, the high pressures of 4.4- the 4th
Filter, 5- proportional pressure control valves, the check valves of 6.1- first, the check valves of 6.2- second, the check valves of 6.3- the 3rd, 6.4- the 4th are unidirectional
Valve, inserted valve of the cover plates of 7.1- first with shuttle valve, inserted valve of the cover plates of 7.2- second with shuttle valve, the cover plates of 7.3- the 3rd are with shuttle valve
Inserted valve, inserted valves of the cover plate with shuttle valve of 7.4- the 4th, the high frequency sound proportional servo valve of 8.1- first band pressure difference compensations, 8.2-
The two high frequency sound proportional servo valves with pressure difference compensation, high frequency sound proportional servo valves of the 8.3- the 3rd with pressure difference compensation, 8.4- the 4th
High frequency sound proportional servo valve with pressure difference compensation, inserted valves of the cover plate with shuttle valve of 9.1- the 5th, the cover plates of 9.2- the 6th are with shuttle valve
Inserted valve, inserted valves of the cover plate with shuttle valve of 9.3- the 7th, inserted valves of the cover plate with shuttle valve of 9.4- the 8th, the pressure-reducing valves of 10.1- first,
The pressure-reducing valves of 10.2- second, the pressure-reducing valves of 10.3- the 3rd, first liang of position and four-way reversing valve of 11.1-, the second two four-way commutations of 11.2-
Valve, the 3rd liang of position and four-way reversing valve of 11.3-, 12.1- first are superimposed throttle grverning valve, and 12.2- second is superimposed throttle grverning valve,
12.3- the 3rd is superimposed throttle grverning valve, 13- top petrol tanks, the ball relief valves of 14.1- first, the ball relief valves of 14.2- second, 14.3-
3rd ball relief valve, the quick liquid filling valves of 15.1- first, the quick liquid filling valves of 15.2- second, the quick liquid filling valves of 15.3- the 3rd,
Magnetic hysteresis telescopic displacement sensor built in 16.1- first, magnetic hysteresis telescopic displacement sensor built in 16.2- second, the plungers of 17- first
Cylinder, 18.1- first piston cylinders, 18.2- second piston cylinders, 19- fast draining valves, P- principal pressure oil pipes, the main oil return pipes of T-, X- controls
Liquefaction pipe, L- drain masts.
Embodiment
To make the object, technical solutions and advantages of the present invention clearer, technical scheme will be carried out below
Detailed description.Obviously, described embodiment is only part of the embodiment of the present invention, rather than whole embodiments.Base
Embodiment in the present invention, those of ordinary skill in the art are resulting on the premise of creative work is not made to be owned
Other embodiment, belong to the scope that the present invention is protected.
Technical scheme is described in detail below in conjunction with the accompanying drawings.
A kind of isothermal die forging process hydraulic system of press, including working end are connected to the first plunger case 17 of sliding block upper center,
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 loops, die forging loop, relief circuit, sliding block backhaul loop,
The He of magnetic hysteresis telescopic displacement sensor 16.1 built in first is respectively equipped with first piston cylinder 18.1 and second piston cylinder 18.2
Magnetic hysteresis telescopic displacement sensor 16.2 built in second；
No.1 piston cylinder driving circuit includes oil inlet and is attached to the first pressure-reducing valve 10.1 on principal pressure oil pipe P, is attached to the
First liang of position and four-way reversing valve 11.1 on the oil-out of one pressure-reducing valve 10.1, it is fuel-displaced to be attached to first liang of position and four-way reversing valve 11.1
The first superposition throttle grverning valve 12.1 on mouth, the first quick liquid filling valve being attached on the first superposition throttle grverning valve 12.1
15.1, the rodless cavity of the liquid outlet and first piston cylinder 18.1 of the first quick liquid filling valve 15.1 is connected, the first quick liquid filling valve
15.1 inlet couples with top petrol tank 13；
Similarly No. two piston cylinder driving circuits and No. three plunger case loops, and the 3rd of No. three plunger case loops quickly fills
The upper working chamber of the liquid outlet of liquid valve 15.3 and the first plunger case 17 is connected；
Piston cylinder oil return circuit is respectively coupled on the rod chamber of first piston cylinder 18.1 and second piston cylinder 18.2 including B mouths
Inserted valve 9.4 of 8th cover plate with shuttle valve, oil inlet are attached to the 4th on the A mouths of inserted valve 9.4 of the 8th cover plate with shuttle valve
High frequency sound proportional servo valve 8.4 with pressure difference compensation, the oil return opening of the 4th high frequency sound proportional servo valve 8.4 with pressure difference compensation lead to
Cross main oil return pipe T and be attached to fuel tank G；
Die forging loop includes shaft orientation plunger variable pump 1, the big flow proportioning pump being parallel between fuel tank G and principal pressure oil pipe P
2.1st, low discharge proportioning pump 2.2, control oil pump 3, oil inlet are respectively coupled to the first cover plate on principal pressure oil pipe P with shuttle valve
The inserted valve 7.3 of inserted valve 7.2, the 3rd cover plate with shuttle valve of inserted valve 7.1, the second cover plate with shuttle valve, oil inlet couple respectively
To inserted valve 7.1 of first cover plate with shuttle valve, inserted valve 7.2 of second cover plate with shuttle valve, the 3rd inserted valve of the cover plate with shuttle valve
7. high frequency sound proportional servo valve of the high frequency sound proportional servo valve 8.1, second with pressure difference compensation of the first band pressure difference compensation on 3
8.2nd, the 3rd high frequency sound proportional servo valve 8.3 with pressure difference compensation, A mouths are respectively coupled to the high frequency sound ratio of first band pressure difference compensation
Example high frequency sound proportional servo valve 8.2, threeth high frequency sound ratio with pressure difference compensation of the servo valve 8.1, second with pressure difference compensation is watched
Take inserted valve 9.1, sixth cover plate inserted valve 9.2 with shuttle valve of the 5th cover plate on valve 8.3 with shuttle valve, the 7th cover plate band shuttle valve
Inserted valve 9.3, inserted valve 9.1, sixth cover plate inserted valve 9.2 with shuttle valve, seventh cover plate of the 5th cover plate with shuttle valve
The B mouths of inserted valve 9.3 with shuttle valve are respectively coupled to the rod chamber of first piston cylinder 18.1, the rod chamber of second piston cylinder 18.2
And first plunger case 17 upper working chamber；
Relief circuit include inlet respectively the rodless cavity with first piston cylinder 18.1, second piston cylinder 18.2 rodless cavity and
The joining fast draining valve 19 of upper working chamber of first plunger case 17, the oil return opening of fast draining valve 19 and main oil return pipe T
Connection；
Sliding block backhaul loop includes No.1 piston cylinder driving circuit, No. two piston cylinder driving circuits, No. three plunger case loops and
Piston cylinder oil return circuit, and the A mouths of inserted valve 7.4 of the 4th cover plate with shuttle valve are connected with principal pressure oil pipe P, top petrol tank 13
Fuel tank G is attached to 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 couples, and unloading port couples with drain mast L；The drain tap of inserted valve 9.1 of 5th cover plate with shuttle valve couples with drain mast L.First
10.1, first liang of position and four-way reversing valves 11.1 and first of pressure-reducing valve are superimposed throttle grverning valve 12.1 and are superimposed, the first lid
The inserted valve 7.1 of strip shuttle valve and the high frequency sound proportional servo valve 8.1 of first band pressure difference compensation can integrate, and first
10.1, first liang of position and four-way reversing valves 11.1, first of pressure-reducing valve are superimposed throttle grverning valve 12.1, inserting of first cover plate with shuttle valve
Valve 7.1, inserted valve 9.1 of the cover plate with shuttle valve of high frequency sound proportional servo valve 8.1 and the 5th of first band pressure difference compensation 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 loops.
Further, relief circuit is as shown in Fig. 2 the control port of fast draining valve 19 couples with control oil pipe X, quickly
Inserted valve 7.4, fourth high frequency sound proportional servo valve 8.4 and eightth with pressure difference compensation of the cover plate of tapping valve 19 and the 4th with shuttle valve
Inserted valve 9.4 of the cover plate 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 each inserted valve of the cover plate 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 big flow proportioning pump 2.1 and principal pressure the oil pipe P
The check valve 6.2 of device 4.2 and second, the 3rd high pressure filter has been sequentially connected in series between low discharge proportioning pump 2.2 and principal pressure oil pipe P
4.3 and the 3rd 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, the 3rd 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, the 3rd 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 frequencies of 16.2+ built in the first high frequency sounds of displacement sensor 16.1+ proportional servo valve 8.1 and second
Ring proportional servo valve 8.2 and realize accurate control to respectively constitute position closed loop；The grading control of flow mainly passes through big flow
Proportioning pump 2.1, the parallel drive of low discharge proportioning pump 2.2+ shaft orientation plunger variable pumps 1 and with the high frequency sound of first band pressure difference compensation
High frequency sound proportional servo valve 8.2, threeth high frequency sound ratio with pressure difference compensation of the proportional servo valve 8.1, second with pressure difference compensation
The Collaborative Control of servo valve 8.3 meets the requirement of two kinds of operating modes of low speed heavy pressure low discharge and high velocity, low pressure big flow, ensure that
The low-speed stable operation of warm die forging machine；The stepless change passing ratio overflow valve 5 of main system pressure is realized.Forging process,
Slide block down velocity interval is 0.005mm/s -10mm/s, and rate request scope is bigger, and maximum speed is compared with minimum speed
Compared with, numerically for difference 2000 times；Moreover, the flow control of proportional servo valve is in opening degree maximum and opening degree minimum, it is defeated
Enter the linear relationship unobvious of electric current and output flow, be difficult to by single proportional servo valve to be controlled to ram speed
Reach actual demand.So the invention uses the high frequency of big flow proportioning pump 2.1, low discharge proportioning pump 2.2+ with pressure difference compensation
Proportional servo valve Collaborative Control is rung, proportioning pump and proportional servo valve can works under the operating mode of high-pressure low-flow so as to ensure that
Make in the range of linearity.The backhaul of sliding block is realized by first piston cylinder 18.1, the rod chamber oil-feed of second piston cylinder 18.2.First
The ratio between the work area of plunger case 17 and first piston cylinder 18.1, the work area of second piston cylinder 18.2 are 2:1.
The process chart of isothermal die forging process is as shown in figure 4, mainly include：Quick pressure, die forging, isothermal die forging process, pressurize rank
Section, off-load, at a slow speed quick return, backhaul.
When sliding block fast downlink, the hydraulic oil in principal pressure oil pipe P is depressurized by the first pressure-reducing valve 10.1, second respectively
Valve 10.2, the 3rd pressure-reducing valve 10.3, first liang of 11.1, second liang of position and four-way reversing valve position and four-way reversing valve 11.2, the 3rd two
Four-way reversing valve 11.3, the first superposition throttle grverning valve 12.1, second are superimposed throttle grverning valve the 12.2, the 3rd and are superimposed throttle grverning
Valve 12.3, open the first quick liquid filling valve 15.1, the second quick liquid filling valve 15.2, the 3rd quick liquid filling valve 15.3, top petrol tank
13 hydraulic oil is fast by the first quick liquid filling valve 15.1, the second quick liquid filling valve 15.2, the 3rd quick liquid filling valve 15.3 respectively
Speed enters the rodless cavity of first piston cylinder 18.1, on the rodless cavity of second piston cylinder 18.2 and the first plunger case 17 in working chamber, drives
Movable slider fast downlink, the speed that quick liquid filling valve is opened can be superimposed by the first superposition throttle grverning valve 12.1, second and saved
Stream flow speed control valve the 12.2, the 3rd is superimposed throttle grverning valve 12.3 and is adjusted respectively.The rod chamber of first piston cylinder 18.1 and the simultaneously
Hydraulic oil in the rod chamber of two piston cylinder 18.2 passes through inserted valve 9.4 of the 8th cover plate 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 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 transducer, the first quick liquid filling valve 15.1, the second quick topping up
Valve 15.2, the 3rd quick liquid filling valve 15.3 are closed rapidly, shaft orientation plunger variable pump 1, big flow proportioning pump 2.1, low discharge ratio
Pump 2.2 is rapidly by hydraulic oil by the first high pressure filter 4.1, the second high pressure filter 4.2, the 3rd high pressure filter 4.3, the
One check valve 6.1, the second check valve 6.2, the 3rd check valve 6.3 be flowed into principal pressure oil pipe P, then principal pressure oil pipe P
Hydraulic oil passes through inserted valve 7.1 of first cover plate with shuttle valve, inserted valve 7.2 of second cover plate with shuttle valve, the 3rd cover plate 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 with pressure difference compensation of first band pressure difference compensation
High frequency sound proportional servo valve 8.3 and fiveth cover plate inserted valve 9.1 with shuttle valve of the example servo valve the 8.2, the 3rd with pressure difference compensation,
Inserted valve 9.2, seventh cover plate inserted valve 9.3 with shuttle valve of 6th cover plate with shuttle valve, quickly enters the nothing of first piston cylinder 18.1
Driving sliding block continues traveling downwardly carry out die forging in working chamber on rod cavity, the rodless cavity of second piston cylinder 18.2 and the first plunger case 17.Mould
The speed of forging is 0.5 ~ 10mm/s, can pass through the ratio electricity for the high frequency sound proportional servo valve 8.1 for controlling first band pressure difference compensation
Proportion electro-magnet BY3, the 3rd height 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 enter each hydraulic cylinder fluid number enter
Individually regulation, the size of proportional servo valve valve core opening degree are directly proportional to size of current for row.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 positional precision of the position closed loop to sliding block
Adjustment in real time is carried out to meet actual process requirement.In die forging process, reference is used as using the output displacement of first piston cylinder 18.1
Value, the output displacement of second piston cylinder 18.2 with its compare generation deviation when, displacement transducer by the data feedback detected to
Industrial control computer, after calculation process, control electric current signal is transmitted to each high frequency sound proportional servo valve respectively, so it is right
The opening degree of each high frequency sound proportional servo is adjusted, and so as to ensure that being synchronized with the movement 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, axially
The off-load of plunger variable pump 1, in high frequency sound of the high frequency sound proportional servo valve 8.1, second with pressure difference compensation of first band pressure difference compensation
High frequency sound proportional servo valve 8.3 and fourth high frequency sound ratio with pressure difference compensation of the proportional servo valve the 8.2, the 3rd with pressure difference compensation
In the case that example servo valve 8.4 is operated in linear zone, controlled by adjusting big flow proportioning pump 2.1 and low discharge proportioning pump 2.2
The input size of voltage meets the needs of actual condition, ratio pump output flow number with the size of input control voltage into
Direct ratio, when isothermal forging speed is 0.005 mm/s, low discharge proportioning pump 2.2 is only needed to work；When isothermal forging speed is 0.5
During mm/s, big flow proportioning pump 2.1 and low discharge proportioning pump 2.2 simultaneously participate in work；When isothermal forging speed is 0.005 mm/
During the mm/s sections of s -0.5, two proportioning pumps can work simultaneously, can also a proportioning pump work independently, according to actual work
Condition demand, flow are supplied on demand.The work area of first plunger case 17 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 actual forging and stamping workpiece, different combinations can be chosen
It is operated：The first plunger case 17 works independently during slide block down, and first piston cylinder 18.1, second piston cylinder 18.2 are servo-actuated, only
Worked in backhaul；First piston cylinder 18.1, second piston cylinder 18.2 work respectively during 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 during slide block down；Three kinds of hydraulic pressure
The combination of cylinder different operating mode can realize the operating pressure output of three kinds of different gradients, and operating pressure realizes defeated on demand
Go out, avoid the waste of the energy.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 operating cylinder inner high voltage oil, when avoiding system release high pressure
Compression shock.
When sliding block backhaul, principal pressure oil pipe P hydraulic oil is by inserted valve 7.4 of the 4th cover plate with shuttle valve, and
Four inserted valves 9.4 of the cover plate with shuttle valve of high frequency sound proportional servo valve 8.4 and the 8th with pressure difference compensation, quickly enter first piston
Driving sliding block quick return, the speed of sliding block quick return can lead in the rod chamber of cylinder 18.1 and the rod chamber of second piston cylinder 18.2
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 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 subtracts by first respectively
Pressure valve 10.1, the second pressure-reducing valve 10.2, the 3rd 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, the 3rd liang of position and four-way reversing valve 11.3, the first superposition throttle grverning valve 12.1, second is superimposed throttle grverning valve
12.2nd, the 3rd superposition throttle grverning valve 12.3, it is fast to open the first quick liquid filling valve 15.1, the second quick liquid filling valve the 15.2, the 3rd
Fast replenishing valve 15.3, working chamber on the rodless cavity of first piston cylinder 18.1, the rodless cavity of second piston cylinder 18.2 and the first plunger case 17
Interior hydraulic oil is flowed back in top petrol tank 13 by respective quick liquid filling valve respectively, sliding block quick return.When sliding block quickly returns
Journey to displacement transducer position setting value when, the first quick liquid filling valve 15.1, the second quick liquid filling valve the 15.2, the 3rd quickly fill
Liquid valve 15.3 is closed rapidly, working chamber, the rodless cavity of first piston cylinder 18.1 and the nothing of second piston cylinder 18.2 on the first plunger case 17
Hydraulic oil in rod cavity passes through inserted valve 9.1 of the 5th cover plate with shuttle valve, inserted valve 9.2 of the 6th cover plate with shuttle valve, respectively
Inserted valve 9.3 of seven cover plates 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 high frequency sound proportional servo valve 8.3 of the high frequency sound proportional servo valve 8.2 and the 3rd with pressure difference compensation flows back to fuel tank respectively.
At a slow speed the speed of backhaul can by the proportion electro-magnet BY2 of the high frequency sound proportional servo valve 8.1 for controlling first band pressure difference compensation,
The proportion electro-magnet BY4 of the second high frequency sound proportional servo valve 8.2 with pressure difference compensation, the 3rd high frequency sound ratio with pressure difference compensation
The proportion electro-magnet BY6 of servo valve 8.3 obtain electric current size each oil circuit is flowed back to fuel tank fluid how much carry out lists
Solely regulation, the size of high frequency sound proportional servo valve valve core opening degree are 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 positional precision of block is adjusted in real time, ensures the synchronism of hydraulic cylinder in return stroke.When sliding block at a slow speed backhaul to limes superiors
During position, isothermal die forging process press is stopped or circulated next time.
The foregoing is only a specific embodiment of the invention, but protection scope of the present invention is not limited thereto, any
Those familiar with the art the invention discloses technical scope in, change or replacement can be readily occurred in, should all be contained
Cover 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, it is characterised in that be connected to the first of sliding block upper center including working end
Plunger case（17）, piston rod is connected to the first piston cylinder at both ends above sliding block（18.1）With second piston cylinder（18.2）,
No.1 piston cylinder driving circuit, No. two piston cylinder driving circuits, No. three plunger case loops, die forging loop, relief circuit, sliding block return
Range loop,
First piston cylinder（18.1）With second piston cylinder（18.2）Inside it is respectively equipped with magnetic hysteresis telescopic displacement sensor built in first
（16.1）With second built in magnetic hysteresis telescopic displacement sensor（16.2）；
No.1 piston cylinder driving circuit is attached to principal pressure oil pipe including oil inlet（P）On the first pressure-reducing valve（10.1）, connection
To the first pressure-reducing valve（10.1）First liang of position and four-way reversing valve on oil-out（11.1）, it is attached to first liang of position and four-way reversing valve
（11.1）The first superposition throttle grverning valve on oil-out（12.1）, it is attached to the first superposition throttle grverning valve（12.1）On
One quick liquid filling valve（15.1）, the first quick liquid filling valve（15.1）Liquid outlet and first piston cylinder（18.1）Rodless cavity be connected
Connect, the first quick liquid filling valve（15.1）Inlet and top petrol tank（13）Connection；
Similarly No. two piston cylinder driving circuits and No. three plunger case loops, and the 3rd of No. three plunger case loops quickly fills
Liquid valve（15.3）Liquid outlet and the first plunger case（17）Upper working chamber be connected；
Piston cylinder oil return circuit is respectively coupled to first piston cylinder including B mouths（18.1）With second piston cylinder（18.2）Rod chamber
On the 8th inserted valve of the cover plate with shuttle valve（9.4）, oil inlet is attached to the 8th inserted valve of the cover plate with shuttle valve（9.4）A mouths
On the 4th high frequency sound proportional servo valve with pressure difference compensation（8.4）, the 4th high frequency sound proportional servo valve with pressure difference compensation
（8.4）Oil return opening pass through main oil return pipe（T）It is attached to fuel tank（G）；
Die forging loop includes being parallel to fuel tank（G）With principal pressure oil pipe（P）Between shaft orientation plunger variable pump（1）, big flow ratio
Example pump（2.1）, low discharge proportioning pump（2.2）, control oil pump（3）, oil inlet is respectively coupled to principal pressure oil pipe（P）On first
Inserted valve of the cover plate with shuttle valve（7.1）, inserted valve of second cover plate with shuttle valve（7.2）, the 3rd inserted valve of the cover plate with shuttle valve（7.
3）, oil inlet is respectively coupled to inserted valve of first cover plate with shuttle valve（7.1）, inserted valve of second cover plate with shuttle valve（7.2）,
Inserted valve of three cover plates with shuttle valve（7. 3）On first band pressure difference compensation high frequency sound proportional servo valve（8.1）, it is second with pressure
The high frequency sound proportional servo valve of difference compensation（8.2）, the 3rd high frequency sound proportional servo valve with pressure difference compensation（8.3）, A mouths join respectively
It is connected to the high frequency sound proportional servo valve of first band pressure difference compensation（8.1）, the second high frequency sound proportional servo valve with pressure difference compensation
（8.2）, the 3rd high frequency sound proportional servo valve with pressure difference compensation（8.3）On the 5th inserted valve of the cover plate with shuttle valve（9.1）,
Inserted valve of six cover plates with shuttle valve（9.2）, the 7th inserted valve of the cover plate with shuttle valve（9.3）, the 5th cover plate inserting with shuttle valve
Fill valve（9.1）, the 6th inserted valve of the cover plate with shuttle valve（9.2）, the 7th inserted valve of the cover plate with shuttle valve（9.3）B mouths join respectively
It is connected to first piston cylinder（18.1）Rod chamber, second piston cylinder（18.2）Rod chamber and the first plunger case（17）Upper work
Make chamber；
Relief circuit include inlet respectively with first piston cylinder（18.1）Rodless cavity, second piston cylinder（18.2）Rodless cavity
And first plunger case（17）The joining fast draining valve of upper working chamber（19）, the fast draining valve（19）Oil return opening with
Main oil return pipe（T）Connection；
Sliding block backhaul loop includes No.1 piston cylinder driving circuit, No. two piston cylinder driving circuits, No. three plunger case loops and
Piston cylinder oil return circuit, and the 4th inserted valve of the cover plate with shuttle valve（7.4）A mouths and principal pressure oil pipe（P）It is connected, high-order oil
Case（13）Pass through drain mast（L）It is attached to fuel tank（G）.
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109751289A (en) * | 2019-01-21 | 2019-05-14 | 太原理工大学 | A kind of hybrid radial forging machine hydraulic system of fluid power |
| CN114165487A (en) * | 2021-12-16 | 2022-03-11 | 合肥合锻智能制造股份有限公司 | Hydraulic control system for composite material |
| CN114321107A (en) * | 2021-11-12 | 2022-04-12 | 武汉船用机械有限责任公司 | Hydraulic control driving system |
| CN116967386A (en) * | 2023-09-25 | 2023-10-31 | 太原理工大学 | Material taking robot for large shaft forgings |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109751289A (en) * | 2019-01-21 | 2019-05-14 | 太原理工大学 | A kind of hybrid radial forging machine hydraulic system of fluid power |
| CN109751289B (en) * | 2019-01-21 | 2020-07-03 | 太原理工大学 | Hydraulic system of hydraulic hybrid radial forging machine |
| CN114321107A (en) * | 2021-11-12 | 2022-04-12 | 武汉船用机械有限责任公司 | Hydraulic control driving system |
| CN114321107B (en) * | 2021-11-12 | 2023-08-18 | 武汉船用机械有限责任公司 | Hydraulic control driving system |
| CN114165487A (en) * | 2021-12-16 | 2022-03-11 | 合肥合锻智能制造股份有限公司 | Hydraulic control system for composite material |
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| CN116967386A (en) * | 2023-09-25 | 2023-10-31 | 太原理工大学 | Material taking robot for large shaft forgings |
| CN116967386B (en) * | 2023-09-25 | 2023-12-08 | 太原理工大学 | Material taking robot for large shaft forgings |
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| CN107504020B (en) | 2019-02-26 |
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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 |