CN113898623A - Hydraulic system, control system and control method of multifunctional forging hydraulic press - Google Patents
Hydraulic system, control system and control method of multifunctional forging hydraulic press Download PDFInfo
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- CN113898623A CN113898623A CN202111091927.7A CN202111091927A CN113898623A CN 113898623 A CN113898623 A CN 113898623A CN 202111091927 A CN202111091927 A CN 202111091927A CN 113898623 A CN113898623 A CN 113898623A
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- 238000000034 method Methods 0.000 title claims abstract description 58
- 238000005242 forging Methods 0.000 title claims abstract description 51
- 230000008569 process Effects 0.000 claims abstract description 41
- 238000006073 displacement reaction Methods 0.000 claims abstract description 31
- 238000010275 isothermal forging Methods 0.000 claims abstract description 29
- 238000001125 extrusion Methods 0.000 claims abstract description 13
- 238000012545 processing Methods 0.000 claims abstract description 9
- 239000003921 oil Substances 0.000 claims description 127
- 239000007788 liquid Substances 0.000 claims description 18
- 238000003825 pressing Methods 0.000 claims description 16
- 239000010727 cylinder oil Substances 0.000 claims description 11
- 230000007935 neutral effect Effects 0.000 claims description 7
- 230000009471 action Effects 0.000 claims description 5
- 230000009467 reduction Effects 0.000 claims description 5
- 238000012937 correction Methods 0.000 claims description 3
- 238000007599 discharging Methods 0.000 claims description 2
- 101000775102 Homo sapiens Transcriptional coactivator YAP1 Proteins 0.000 description 8
- 102100031873 Transcriptional coactivator YAP1 Human genes 0.000 description 8
- 101100001798 Saccharomyces cerevisiae (strain ATCC 204508 / S288c) CAD1 gene Proteins 0.000 description 5
- 238000013461 design Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000009191 jumping Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 229910000861 Mg alloy Inorganic materials 0.000 description 1
- 229910001069 Ti alloy Inorganic materials 0.000 description 1
- 229910045601 alloy Inorganic materials 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
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- 238000004519 manufacturing process Methods 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
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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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
- B21J9/00—Forging presses
- B21J9/10—Drives for forging presses
- B21J9/12—Drives for forging presses operated by hydraulic or liquid pressure
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
- B21J9/00—Forging presses
- B21J9/10—Drives for forging presses
- B21J9/20—Control devices specially adapted to forging presses not restricted to one of the preceding subgroups
-
- 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
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Presses (AREA)
Abstract
The invention discloses a hydraulic system, a control system and a control method of a multifunctional forging hydraulic press, belonging to the technical field of forging hydraulic presses and being characterized in that an oil supply part comprises a plurality of sets of quantitative supply oil ways and variable supply oil ways; the power part comprises three hydraulic cylinders; the data acquisition part comprises a displacement sensor for acquiring the position information of the slide block, two side cylinder pressure sensors for acquiring pressure parameters of the left hydraulic cylinder and the right hydraulic cylinder, and a middle cylinder pressure sensor for acquiring pressure parameters of the middle hydraulic cylinder; the control section includes: the system comprises a process selection module, a data receiving module and a first data processing module, wherein the first data processing module is used for calculating the real-time speed of a sliding block according to the position data of the sliding block; and the second data processing module is used for controlling the flow of the output constant delivery pump and the output proportional pump and the flow of the high-frequency corresponding directional valve according to the position data of the slide block and the pressure parameters of the three hydraulic cylinders. The three forging processes of free forging, precision extrusion forging and isothermal forging can be realized on one hydraulic press.
Description
Technical Field
The invention belongs to the technical field of forging hydraulic presses, and particularly relates to a hydraulic system, a control system and a control method of a multifunctional forging hydraulic press.
Background
In recent years, with the rapid development of the fields of aerospace, nuclear power, wind power and the like in China, the demand of a forging hydraulic press is continuously increased along with the increase of various forgings required by the fields. The control system of the traditional hydraulic machine can only meet the single forging functions of free forging or die forging and the like, a user often needs to purchase a multi-state hydraulic machine to meet the requirements of different types of forgings in the terminal market, the multifunctional forging hydraulic machine is developed to meet the requirements of different processes of free forging, precision extrusion, isothermal forging and the like of the user, the equipment purchase cost of a forge piece production user can be saved, meanwhile, the terminal users in different fields can be met, and therefore the design and development of the control system and the control method of the multifunctional forging hydraulic machine have very important significance.
Disclosure of Invention
The invention provides a hydraulic system, a control system and a control method of a multifunctional forging hydraulic press for solving the technical problems in the prior art, and can realize three forging processes of free forging, precise extrusion forging and isothermal forging of products such as aluminum alloy, magnesium alloy, titanium alloy, high-temperature alloy and the like on the same hydraulic press.
A first object of the present invention is to provide a hydraulic system of a multi-functional forging hydraulic press, comprising:
the oil supply part comprises at least eight independent quantitative supply oil ways and three variable supply oil ways;
the power part comprises three hydraulic cylinders for driving the sliding block to move up and down; the three hydraulic cylinders are respectively a left hydraulic cylinder, a middle hydraulic cylinder and a right hydraulic cylinder, and the middle hydraulic cylinder is positioned in the middle of the left hydraulic cylinder and the right hydraulic cylinder; wherein:
the oil supply part is connected with oil inlets of the two oil inlet pipelines through a main pipeline, and an oil outlet of the oil inlet pipeline A is connected with an oil inlet of the middle hydraulic cylinder through a relay pipeline A; an oil outlet of the oil inlet pipeline B is respectively connected with oil inlets of the left hydraulic cylinder and the right hydraulic cylinder through a relay pipeline B; an isothermal forging high-frequency corresponding directional valve is installed on the oil inlet pipeline A, and a main pipeline pressure relief proportional servo valve is installed on the oil inlet pipeline B; the relay pipeline A is provided with a middle cylinder oil inlet electromagnetic valve, and the relay pipeline B is provided with two side cylinder oil inlet electromagnetic valves; the oil inlet of each hydraulic cylinder is connected with an oil tank through a pressure relief pipeline; a pressure relief proportional servo valve is arranged on the pressure relief pipeline; the oil outlets of the left hydraulic cylinder and the right hydraulic cylinder are connected with a main pipeline through return pipelines, and a slider lower cavity proportional servo valve and a slider return electromagnetic valve are installed on the return pipelines.
Preferably, each set of quantitative oil supply circuit comprises a quantitative pump set and a motor.
Preferably, each set of variable oil supply circuit comprises a proportional pump set and a motor.
A second object of the present invention is to provide a control system of a multi-function hydraulic forging press, for controlling the operating state of the hydraulic system, comprising:
the data acquisition part comprises a displacement sensor for acquiring the position information of the slide block, two side cylinder pressure sensors for acquiring the pressure parameters of the left hydraulic cylinder and the right hydraulic cylinder, and a middle cylinder pressure sensor for acquiring the pressure parameter of the middle hydraulic cylinder;
a control section including:
the process selection module comprises a free forging process module, a precision extrusion process module and an isothermal forging process module;
a data receiving module for reading the position data of the slide block and the pressure parameters of the three hydraulic cylinders;
the first data processing module is used for calculating the real-time speed of the sliding block according to the position data of the sliding block;
and the second data processing module is used for controlling the flow of the output constant delivery pump and the output proportional pump and the flow of the high-frequency corresponding directional valve according to the position data of the slide block and the pressure parameters of the three hydraulic cylinders.
The third purpose of the invention is to provide a control method of the multifunctional forging hydraulic press, which realizes the following steps based on the free forging process module:
defining the slide descending speed provided by each fixed displacement pump as Vq, the maximum slide descending speed provided by each variable displacement pump as Vp, and the opening size of the proportional pump as Xn, wherein Xn is [0, 100% ];
firstly, quickly descending a sliding block;
starting a fast gear descending, setting a fast descending speed Vf1 and a lower cavity oil discharging given function, and giving the size of an opening of a lower cavity proportional servo valve of a sliding block;
prepare for slow down, according to the set slow down pressurization speed Vs1 and the theoretical formula: vs1 ═ N1 × Vq + X11 × Vp + K1 × X12 × Vp, N1 quantitative pumps were turned on; using a first proportional pump, starting a first proportional electromagnet, and setting the opening size X11 of the first proportional pump; judging whether a second proportional pump is used or not, starting a second proportional electromagnet or not, giving the opening size X12 of the second proportional pump, if the second proportional pump is started, setting K1 to 1, and if the second proportional pump is not started, setting K1 to 0;
secondly, the slide block rotates downwards quickly and is pressurized downwards slowly;
starting slow gear descending, setting a slow descending pressurizing speed Vs1 and a descending deceleration curve function, and gradually reducing the opening size of the proportional servo valve of the lower cavity of the given sliding block until the opening size is reduced to a given value of the slow lower opening;
keeping opening N1 constant delivery pump electromagnets and the first proportional electromagnet, setting the opening size X11 of the first proportional pump, and keeping the state of the second proportional electromagnet and setting the opening size X21 of the second proportional pump;
step three, finishing the descending of the sliding block;
closing the constant delivery pump electromagnet and the proportional electromagnet, and closing the oil inlet electromagnetic valves of the cylinders at the two sides and the oil inlet electromagnetic valve of the middle cylinder;
gradually increasing the pressure relief proportional servo valves of the two side cylinders according to the first pressure relief curve function, and gradually increasing the pressure relief proportional servo valves of the middle cylinder according to the second pressure relief curve function until the pressure relief of the three hydraulic cylinders is completed; meanwhile, the main pipeline pressure relief proportional servo valve is gradually increased according to the third pressure relief relation curve until the minimum closing value is given after the pressure relief of the main pipeline is finished;
step four, returning the slide block;
opening the electromagnetic valve for the return stroke of the slide block, and simultaneously opening the electromagnets of the constant delivery pumps one by one until the slide block reaches the set return stroke speed and then keeping the speed return stroke;
step five, finishing the return stroke of the sliding block or performing subsequent actions;
when the return stroke of the slide block reaches a return stroke stop position, the pressing is finished;
in the return stroke process of the sliding block, if the operating handle descends to a high gear, the first step is skipped;
in the return process of the sliding block, if the operating handle descends to a slow gear, the sliding block descends slowly, the constant delivery pumps are started to N1 one by one according to the set slow descending pressurizing speed Vs1, the first proportional electromagnet is started, the opening size X11 of the first proportional pump is given, whether the second proportional electromagnet is started or not is judged, and after the opening size X21 of the second proportional pump is given or not, the oil inlet electromagnetic valves of the two cylinders and the oil inlet electromagnetic valve of the middle cylinder are started; setting the two side cylinder pressure relief proportional servo valves and the middle cylinder pressure relief proportional servo valve as a minimum closing value; and skipping to the third step.
The fourth purpose of the invention is to provide a control method of the multifunctional hydraulic forging press, which is based on the precise extrusion process module and realizes the following steps:
defining the slide descending speed provided by each fixed displacement pump as Vq, the maximum slide descending speed provided by each variable displacement pump as Vp, and the opening size of the proportional pump as Xn, wherein Xn is [0, 100% ];
firstly, quickly descending a sliding block;
starting any one of fast gear descending or slow gear descending, setting a fast descending speed Vf2 and a lower cavity oil discharge given function, and giving the opening size of a sliding block lower cavity proportional servo valve;
prepare for slow down, set the slow down pressurization speed Vs2 and the theoretical equation: vs2 ═ N2 × Vq + X21 × Vp + K1 × X22 × Vp, N2 quantitative pumps were turned on; using a first proportional pump, starting a first proportional electromagnet and setting the opening size X21 of the first proportional pump; judging whether a second proportional pump is used or not, starting a second proportional electromagnet or not, setting the opening size X22 of the second proportional pump, and if the second proportional pump is started, K1 is equal to 1, and if the second proportional pump is not started, K1 is equal to 0;
the three hydraulic cylinders move downwards, negative pressure is generated in the upper cavities of the three hydraulic cylinders, and the liquid filling valve is passively opened for liquid filling;
opening oil inlet electromagnetic valves of the two side cylinders and an oil inlet electromagnetic valve of the middle cylinder, and setting the pressure relief proportional servo valves of the two side cylinders and the pressure relief proportional servo valve of the middle cylinder as a minimum closing value;
secondly, the slide block rotates downwards quickly and is pressurized downwards slowly;
the slide block moves to a set slow down position, and the opening size of the proportional servo valve of the lower cavity of the given slide block is gradually reduced until the opening size is reduced to a given value of the slow down opening according to a set slow down pressurizing speed Vs2 and a descending deceleration curve function;
keeping opening N2 constant delivery pump electromagnets, keeping opening the first proportional electromagnet, performing closed-loop correction on the basis of a theoretical value X11, then setting the opening size X211 of the first proportional pump, and keeping the state of the second proportional electromagnet and the opening size X22 of the second proportional pump;
step three, the pressure is released after the sliding block stops descending or the pressure maintaining is finished;
closing the constant delivery pump electromagnet and the proportional electromagnet, and closing the oil inlet electromagnetic valves of the cylinders at the two sides and the oil inlet electromagnetic valve of the middle cylinder;
gradually increasing the pressure relief proportional servo valves of the two side cylinders according to the first pressure relief curve function, and gradually increasing the pressure relief proportional servo valves of the middle cylinder according to the second pressure relief curve function until the pressure relief of the three hydraulic cylinders is completed; meanwhile, the main pipeline pressure relief proportional servo valve is gradually increased according to a third pressure relief relation curve until the main pipeline pressure relief is finished and then a minimum closing value is set;
step four, returning the slide block;
and after the operating handle is shifted to the return stroke gear of the sliding block, the operating handle is reset to a neutral position, the electromagnetic valve for return stroke of the sliding block is opened, and meanwhile, the electromagnets of the constant delivery pump are opened one by one until the sliding block reaches the set return stroke speed, and the speed return stroke is kept until the sliding block stops.
The fifth purpose of the invention is to provide a control method of the multifunctional forging hydraulic press, which is based on the isothermal forging process module and realizes the following steps:
defining the slide descending speed provided by each fixed displacement pump as Vq, the maximum slide descending speed provided by each variable displacement pump as Vp, and the opening size of the proportional pump as Xn, wherein Xn is [0, 100% ];
firstly, quickly descending a sliding block;
starting any one of fast gear descending or slow gear descending, setting a fast descending speed Vf2 and a lower cavity oil discharge given function, and giving the opening size of a sliding block lower cavity proportional servo valve;
prepare for slow down, according to the set slow down pressurization speed Vs3 and the theoretical formula: when Vs3 is N3 × Vq + X23 × Vp, N3 quantitative pumps are started; using a first proportional pump, starting a first proportional electromagnet, and setting the opening size X31 of the first proportional pump;
the three hydraulic cylinders move downwards, negative pressure is generated in the upper cavities of the three hydraulic cylinders, and the liquid filling valve is passively opened for liquid filling;
opening oil inlet electromagnetic valves of the two side cylinders and an oil inlet electromagnetic valve of the middle cylinder, and setting the pressure relief proportional servo valves of the two side cylinders and the pressure relief proportional servo valve of the middle cylinder as a minimum closing value;
step two, the slide block is rotated from fast downward to slow downward;
the slide block moves to a set slow down position, and the opening size of the proportional servo valve of the lower cavity of the given slide block is gradually reduced until the opening size is reduced to a given value of the slow down opening according to a set slow down pressurizing speed Vs3 and a descending deceleration curve function;
keeping opening N3 constant delivery pump electromagnets, keeping opening a first proportional electromagnet, and setting the opening size X31 of the first proportional pump;
step three, slowly rotating the sliding block to press downwards;
closing the electromagnet of the constant delivery pump;
keeping turning on the first proportional electromagnet, and setting the opening size X3 of the first proportional pump MP 1;
gradually reducing the opening size of the proportional servo valve of the lower cavity of the given slide block until the opening size is reduced to a given value of a pressing descending opening according to a set isothermal forging pressing descending set speed Vs4 and a descending deceleration curve function;
opening the isothermal forging high-frequency corresponding direction valve, outputting the opening size X4 of the isothermal forging high-frequency corresponding direction valve according to the isothermal forging pressing descending set speed Vs4 through a closed-loop control algorithm;
step four, the pressure is released after the sliding block stops descending or the pressure maintaining is finished;
closing the oil inlet electromagnetic valves of the two side cylinders and the oil inlet electromagnetic valve of the middle cylinder;
gradually increasing the pressure relief proportional servo valves of the two side cylinders according to the first pressure relief curve function, and gradually increasing the pressure relief proportional servo valves of the middle cylinder according to the second pressure relief curve function until the pressure relief of the three hydraulic cylinders is completed; meanwhile, the main pipeline pressure relief proportional servo valve is gradually increased according to a third pressure relief relation curve until the main pipeline pressure relief is finished and then a minimum closing value is set;
step five, returning the slide block;
and when the operating handle is shifted to the return stroke position of the sliding block, the operating handle is reset to a neutral position, the electromagnetic valves for return stroke of the sliding block are opened, and meanwhile, the electromagnets of the constant delivery pump are opened one by one until the sliding block reaches the set return stroke speed, and the speed return stroke is kept until the sliding block stops.
Preferably, the pressure of the two-side cylinder pressure sensor and the opening relation function of the two-side cylinder pressure relief proportional servo valve follow the following relation:
wherein p0, p1, p2, p3, p4, p5, a1, a2, A3, a4, a5, K11, K12, K13, K14, K15, and K16 are constants taken in debugging;
the relation function of the pressure of the middle cylinder pressure sensor and the opening of the middle cylinder pressure relief proportional servo valve follows the following relation:
wherein pb0, pb1, pb2, pb3, pb4, pb5, B1, B2, B3, B4, B5, K21, K22, K23, K24, K25, and K26 are constants taken in debugging;
when the hydraulic system is at a high pressure, the opening of the pressure relief proportional servo valve is rapidly increased, the opening is increased in speed to be slowly increased along with the reduction of the pressure, and when the hydraulic system is at a low pressure, the opening of the pressure relief proportional servo valve is rapidly increased.
Preferably, the relationship between the fast descending/slow descending/pressing descending speed of the slide block and the size of the opening of the proportional servo valve in the lower cavity of the slide block is set as a fitting relationship of oil discharge in the lower cavity.
The invention has the advantages and positive effects that:
1. the invention can realize three forging processes of free forging, precise extrusion forging and isothermal forging on one hydraulic press, adopts the combination of a constant delivery pump, a variable delivery pump, a proportional servo valve and the like in the design to realize various process requirements in principle, and reasonably matches the opening and closing of each element and the analog output value thereof aiming at the requirements of each forming stage of each process on speed and pressure in the debugging and running process, thereby not only meeting the precise control of each process action, but also realizing the flexible control of continuous action and switching thereof.
2. In the process that the sliding block slowly falls, a liquid inlet curve (matched with a pump valve) and a liquid discharge curve (matched with a proportional servo valve) are combined, and an oil inlet and oil discharge independent control mode is adopted, so that compared with a traditional constant delivery pump oil inlet overflow valve, the constant delivery pump oil inlet overflow valve is used as a system for supporting oil discharge, the speed control is accurate and continuous, and the speed switching is fast and stable.
3. The oil supply of the invention adopts the combination of the fixed variable pump and the proportional pump, so that the speed regulation in a larger range can be realized, the fixed displacement pump is roughly matched to be close to the target speed range, and the proportional pump realizes the accurate target speed. Compared with the method which completely uses a proportional pump, the method has the advantages of cost reduction and more accurate control compared with the method which completely uses a fixed displacement pump.
Drawings
FIG. 1 is a block diagram of a hydraulic system in accordance with a preferred embodiment of the present invention;
FIG. 2 is a graph of a first pressure relief curve function in accordance with a preferred embodiment of the present invention;
FIG. 3 is a graph of a second pressure relief curve as a function of a preferred embodiment of the present invention;
FIG. 4 is a plot of a third pressure relief curve as a function of a preferred embodiment of the present invention;
FIG. 5 is a graph of a fourth pressure relief curve as a function of a preferred embodiment of the present invention.
In the figure: M1-Mn is a quantitative pump set and a motor thereof, MP1-MPn is a proportional pump set and a motor thereof, BQ1 is a slider displacement sensor, BP91 is a two-side cylinder pressure sensor, BP92 is a middle cylinder pressure sensor, YD81 is a main pipeline pressure relief proportional servo valve, YD82 is a slider lower cavity proportional servo valve, YT91 is an isothermal forging high-frequency corresponding direction valve, YD91a and YD91b are two-side cylinder pressure relief proportional servo valves, YD92 is a middle cylinder pressure relief proportional servo valve, YA1-YAn is a quantitative pump electromagnet, YAP1-YAPn is a proportional electromagnet, YA91 is a two-side cylinder oil inlet electromagnetic valve, YA92 is a middle cylinder oil inlet electromagnetic valve, and YA21 is a slider return electromagnetic valve.
Detailed Description
In order to further understand the contents, features and effects of the present invention, the following embodiments are illustrated and described in detail with reference to the accompanying drawings:
the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments obtained by those skilled in the art without creative efforts based on the technical solutions of the present invention belong to the protection scope of the present invention.
In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention.
Please refer to fig. 1 to 5.
First preferred embodiment:
a hydraulic system of a multifunctional forging hydraulic press comprises an oil supply part and a power part; wherein:
the oil supply part comprises at least eight independent quantitative supply oil ways and three variable supply oil ways; the present preferred embodiment is explained below taking eight independent sets of fixed-quantity oil supply passages and three sets of variable-quantity oil supply passages as an example;
each set of quantitative oil supply circuit comprises a quantitative pump set and a motor, such as M1-Mn in the figure; each set of variable oil supply circuit comprises a proportional pump set and a motor, such as MP1-MPn in the figure.
The power part comprises three hydraulic cylinders for driving the sliding block to move up and down; as shown in the position relation of fig. 1, the three hydraulic cylinders are respectively a left hydraulic cylinder, a middle hydraulic cylinder and a right hydraulic cylinder, and the middle hydraulic cylinder is positioned in the middle of the left hydraulic cylinder and the right hydraulic cylinder; wherein:
the oil supply part is connected with oil inlets of two oil inlet pipelines through a main pipeline, and the two oil inlet pipelines are named as an oil inlet pipeline A and an oil inlet pipeline B respectively; an oil outlet of the oil inlet pipeline A is connected with an oil inlet of the middle hydraulic cylinder through a relay pipeline A; an oil outlet of the oil inlet pipeline B is respectively connected with oil inlets of the left hydraulic cylinder and the right hydraulic cylinder through a relay pipeline B; an isothermal forging high-frequency corresponding directional valve YT91 is installed on the oil inlet pipeline A, and a main pipeline pressure relief proportional servo valve YD81 is installed on the oil inlet pipeline B; the relay pipeline A is provided with a middle cylinder oil inlet electromagnetic valve YA92, and the relay pipeline B is provided with two side cylinder oil inlet electromagnetic valves YA 91; the oil inlet of each hydraulic cylinder is connected with an oil tank through a pressure relief pipeline; a pressure relief proportional servo valve is arranged on the pressure relief pipeline, YD91a and YD91b are proportional servo valves for pressure relief of cylinders on two sides, and YD92 is a proportional servo valve for pressure relief of a middle cylinder; oil outlets of the left hydraulic cylinder and the right hydraulic cylinder are connected with a main pipeline through return pipelines, and a slider lower cavity proportional servo valve YD82 and a slider return electromagnetic valve YA21 are mounted on each return pipeline.
Second preferred embodiment:
a control system for a hydraulic multi-function forging press for controlling the operating state of a hydraulic system in the preferred embodiment, comprising:
the data acquisition part comprises a data acquisition card and a plurality of sensors, wherein the plurality of sensors comprise a slider displacement sensor BQ1 for acquiring slider position information, two side cylinder pressure sensors BP91 for acquiring left hydraulic cylinder and right hydraulic cylinder pressure parameters, and a middle cylinder pressure sensor BP92 for acquiring middle hydraulic cylinder pressure parameters;
a control unit that selects a programmable controller, the control unit including:
the process selection module comprises a free forging process module, a precision extrusion process module and an isothermal forging process module;
a data receiving module for reading the position data of the slide block and the pressure parameters of the three hydraulic cylinders;
the first data processing module is used for calculating the real-time speed of the sliding block according to the position data of the sliding block;
and the second data processing module is used for controlling the flow of the output constant delivery pump and the output proportional pump and the flow of the high-frequency corresponding directional valve according to the position data of the slide block and the pressure parameters of the three hydraulic cylinders. Wherein:
the control part respectively carries out data interaction with the data acquisition part and the hydraulic system through the I/O port.
In the two preferred embodiments described above:
the constant delivery pump and a motor M1-Mn thereof are used for supplying oil fixed by the oil cylinder to enable the sliding block to move, and not less than eight sets of the constant delivery pump and the motor M1-Mn thereof;
the proportional pump and a motor MP1-MPn thereof are used for supplying oil liquid which can be adjusted and controlled by the oil cylinder to enable the sliding block to move, and not less than three sets of the oil liquid are provided;
the slider displacement sensor BQ1 is used for acquiring position data of the slider;
the two-side cylinder pressure sensor BP91 is used for measuring the pressure of the two-side cylinder;
an intermediate cylinder pressure sensor BP92 for measuring an intermediate cylinder pressure;
the slide block lower cavity proportional servo valve YD82 is mainly used for controlling the fast descending speed of the slide block;
a main pipeline pressure relief proportional servo valve YD81, mainly used for main pipeline pressure relief in the system;
the isothermal forging high-frequency corresponding direction valve YT91 is used for supplying adjustable and controllable oil to an oil cylinder to enable a sliding block to move under the isothermal forging process;
two side cylinder pressure relief proportional servo valves YD91a and YD91b for controlling the two side hydraulic cylinders to relieve pressure;
the middle cylinder pressure relief proportional servo valve YD92 is used for controlling the middle hydraulic cylinder to relieve pressure;
the constant delivery pump electromagnets YA1-YAn are used for opening and closing the constant delivery pump flow supply slide block.
Proportional pump electromagnets YAP1-YAPn for turning on and off the proportional pump flow feed slide.
The two-side cylinder oil inlet electromagnetic valve YA91 is used for opening and closing oil inlet of the two-side cylinder;
the middle cylinder oil inlet electromagnetic valve YA92 is used for opening and closing the middle cylinder oil inlet;
the electromagnetic valve YA21 for the return stroke of the slide block is used for controlling the return stroke of the slide block;
and the programmable controller is used for reading the position data of the slide block, calculating the real-time speed of the slide block, and controlling the flow of the output constant delivery pump proportional pump and the flow of the high-frequency corresponding directional valve.
The preferred embodiment can realize three forging processes of free forging, precision extrusion forging and isothermal forging on a 6000-ton multifunctional hydraulic press.
Firstly, defining the descending speed of a slide block provided by each fixed displacement pump as Vq, the maximum descending speed of the slide block provided by each variable displacement pump as Vp, the opening size of a proportional pump as Xn (the value range of Xn is 0, 100%), the pressure obtained by a two-side cylinder pressure sensor BP91 as p91, the pressure obtained by a middle cylinder pressure sensor BP92 as p92, the opening sizes of two-side cylinder pressure-relief proportional servo valves YD91a and YD91B as A, the opening size of a middle cylinder pressure-relief proportional servo valve YD92 as B, the opening size of a main pipeline pressure-relief proportional servo valve YD81 as C, and the opening size of a slide block lower cavity proportional servo valve YD82 as D.
Under the mode that the maximum tonnage is 6000 tons, the slow down speed range of the free forging process sliding block is 0-30mm/s, the slow down speed of the precision extrusion process sliding block is maximally 1-15mm/s, and the slow down speed of the precision extrusion process sliding block is maximally 0.1-1 mm/s.
The slide block descending speed provided by each fixed displacement pump is Vq which is 3.15mm/s, the maximum slide block descending speed provided by each variable displacement pump is Vp which is 3.15mm/s, and the opening size of the proportional pump is Xn (the value range of Xn is Xn which is 0-1).
The free forging process at least comprises the following steps:
step one, quickly moving a sliding block down:
(1) the user pulls down the operating handle to the fast gear to descend, the PLC gives a function according to the set fast descending speed Vf1 and the lower cavity oil discharge, and the opening size of the slider lower cavity proportional servo valve YD82 is given.
(2) The PLC is prepared for slow down, according to the set slow down pressurization speed Vs1 and the theoretical formula: vs1 ═ N1 × Vq + X11 × Vp + K1 × X12 × Vp, the PLC started N1 quantitative pumps; the PLC uses a first proportional pump M1, starts YAP1 and gives the opening size X11 of a first proportional pump MP 1; in order to avoid the dead zone of the proportional pump adjustment, the PLC determines whether to use the second proportional pump MP2, whether to turn on the second proportional electromagnet YAP2 and give the opening size X12 of the second proportional pump MP2, if the opening size K1 is 1, and if the opening size K1 is not 0.
For example: preliminarily calculating the flow rate of 100% which needs to be output by the proportional pump MP1 and is required to be output by the target speed, then outputting X11 to be 80%, starting the proportional pump MP2 and giving a given opening size X12 to be 20%; the preliminary calculation of the target speed requires that the first proportional pump MP1 needs to output a flow rate of 0%, the number of the fixed displacement pumps is 3, the output X11 is 80%, the second proportional pump MP2 is started, the given opening size X12 is 20%, and the output N1 is 2.
(3) At the moment, the main cylinder moves downwards, the upper cavity of the main cylinder generates negative pressure, and the liquid filling valve is passively opened for liquid filling.
(4) The PLC opens the oil inlet electromagnetic valves YA91 of the two side cylinders and the oil inlet electromagnetic valve YA92 of the middle cylinder. The PLC gives the proportional servo valves YD91a, YD91b of the two side cylinders and the proportional servo valve YD92 of the middle cylinder to a minimum closing value.
Step two, the slide block is rotated fast to be pressed slowly:
(1) when a user operates the handle to move downwards to a slow gear, the PLC gradually reduces the opening size of the proportional servo valve YD82 of the lower cavity of the given slide block until the opening size is reduced to a given value of the slow lower opening according to the set slow down pressurizing speed Vs1 and a descending deceleration curve function.
(2) The PLC keeps opening N1 constant delivery pump electromagnets, keeps opening the first proportional electromagnet YAP1 and gives the opening size X11 of the first proportional pump MP1, and keeps the state of the second proportional electromagnet YAP2 and gives the opening size X21 of the second proportional pump MP 2.
Step three, finishing the descending of the sliding block;
and ending the pressing if the slide block reaches the descending stop position or the user resets the handle to the neutral position. If the slide block does not reach the descending stop position, the user operates the handle to reach the return stroke gear of the slide block.
(1) The PLC closes the constant displacement pump electromagnet and the proportional electromagnet, and closes the oil inlet electromagnetic valves YA91 of the two side cylinders and the oil inlet electromagnetic valve YA92 of the middle cylinder.
(2) The PLC gradually increases the pressure relief proportional servo valves YD91a and YD91b of the given two-side cylinder according to the f1 pressure relief curve function, and gradually increases the pressure relief proportional servo valve YD92 of the given middle cylinder according to the f2 pressure relief curve function until the pressure relief of the two-side cylinder and the middle cylinder is finished. Meanwhile, the PLC gradually increases the main pipeline pressure relief proportional servo valve YD81 according to the pressure relief relation curve of g3 until the pressure relief of the main pipeline is finished and then the minimum closing value is set.
Step four, returning the slide block;
the PLC opens the electromagnetic valve YA21 for the slide block return stroke, and simultaneously opens the electromagnets of the constant delivery pumps one by one until the slide block reaches the set return stroke speed and then keeps the speed return stroke.
Step five, finishing or follow-up action of return stroke of the slide block
If the return stroke of the slide block reaches a return stroke stop position, ending the pressing; if the user operates the handle to descend to the fast gear in the return stroke of the sliding block, jumping to the first step; if the user operates the handle to descend to a slow gear in the return process of the sliding block, the sliding block descends slowly, the PLC starts the constant displacement pumps to N1 according to the set slow descending pressurizing speed Vs1, starts the first proportional electromagnet YAP1 and gives the opening size X11 of the first proportional pump MP1, and after judging whether the second proportional electromagnet YAP2 is started and whether the opening size X21 of the second proportional pump MP2 is given, the PLC starts the oil inlet electromagnetic valves YA91 of the two side cylinders and the oil inlet electromagnetic valve YA92 of the middle cylinder. The PLC gives the proportional servo valves YD91a, YD91b of the two side cylinders and the proportional servo valve YD92 of the middle cylinder to a minimum closing value. And jumping to the step three to-and-fro circulation.
The precision extrusion process at least comprises the following steps:
step one, the sliding block is quickly moved down.
(1) The user pulls down the operating handle to any one of the fast gear descending or the slow gear descending, and the PLC gives the opening size of the slider lower cavity proportional servo valve YD82 according to the set fast descending speed Vf2 and the lower cavity oil discharge given function.
(2) The PLC is prepared for slow down, according to the set slow down pressurization speed Vs2 and the theoretical formula: vs2 ═ N2 × Vq + X21 × Vp + K1 × X22 × Vp, the PLC started N2 quantitative pumps; the PLC uses a first proportional pump MP1, turns on a first proportional electromagnet YAP1 and gives an opening size X21 of a first proportional pump MP 1; in order to avoid the dead zone of proportional pump adjustment, the PLC judges whether a second proportional pump MP2 is used or not, whether a second proportional electromagnet YAP2 is started or not, and the opening size X22 of the second proportional pump MP2 is given, if the opening size K1 is 1, and if the opening size K1 is not 0;
(3) at the moment, the three hydraulic cylinders move downwards, the upper cavities of the three hydraulic cylinders generate negative pressure, and the liquid filling valves are passively opened for liquid filling.
(4) The PLC opens the oil inlet electromagnetic valves YA91 of the two side cylinders and the oil inlet electromagnetic valve YA92 of the middle cylinder. The PLC gives the proportional servo valves YD91a, YD91b of the two side cylinders and the proportional servo valve YD92 of the middle cylinder to a minimum closing value.
Step two, the slide block is rotated fast to be pressed slowly:
(1) when the slide block runs to a set slow down position, the PLC gradually reduces the opening size of the proportional servo valve YD82 of the lower cavity of the given slide block until the opening size is reduced to a set slow down opening value according to the set slow down pressurizing speed Vs2 and a descending deceleration curve function.
(2) The PLC keeps turning on N2 constant delivery pump electromagnets, keeps turning on the first proportional electromagnet YAP1, gives the opening size X211 of the first proportional pump MP1 after closed-loop correction is carried out on the basis of the theoretical value X11, and keeps keeping the state of the second proportional electromagnet YAP2 and the opening size X22 of the second proportional pump MP 2.
Step three, releasing pressure after the slide block stops descending or pressure maintaining is finished
And the slide block reaches a descending stop position in a fixed distance mode or maintains the pressure after the slide block is pressurized to a set tonnage in a fixed pressure mode.
(1) The PLC closes the constant displacement pump electromagnet and the proportional electromagnet, and closes the oil inlet electromagnetic valves YA91 of the two side cylinders and the oil inlet electromagnetic valve YA92 of the middle cylinder.
(2) The PLC gradually increases the pressure relief proportional servo valves YD91a and YD91b of the given two-side cylinder according to the f1 pressure relief curve function, and gradually increases the pressure relief proportional servo valve YD92 of the given middle cylinder according to the f2 pressure relief curve function until the pressure relief of the two-side cylinder and the middle cylinder is finished. Meanwhile, the PLC gradually increases the main pipeline pressure relief proportional servo valve YD81 according to the pressure relief relation curve of g3 until the pressure relief of the main pipeline is finished and then the minimum closing value is set.
Step four, the return stroke of the slide block
When the user operates the handle to return to the neutral position after the slide block returns to the return gear position, the PLC opens the electromagnetic valve YA21 for the return stroke of the slide block, and simultaneously opens the electromagnets of the constant displacement pump one by one until the slide block reaches the set return speed, and then the speed is maintained to return to stop.
2.3 the isothermal forging process at least comprises the following steps:
step one, the sliding block is quickly moved down.
(1) The user pulls down the operating handle to any one of the fast gear descending or the slow gear descending, and the PLC gives the opening size of the slider lower cavity proportional servo valve YD82 according to the set fast descending speed Vf3 and the lower cavity oil discharge given function.
(2) The PLC is prepared for slow down, according to the set slow down pressurization speed Vs3 and the theoretical formula: vs3 ═ N3 × Vq + X23 × Vp, the PLC turned on N3 fixed displacement pumps; the PLC uses a first proportional pump MP1, turns on a first proportional electromagnet YAP1 and gives an opening size X31 of a first proportional pump MP1 (the precision is not high, and MP2 is not needed);
(3) at the moment, the three hydraulic cylinders move downwards, the upper cavities of the three hydraulic cylinders generate negative pressure, and the liquid filling valves are passively opened for liquid filling.
(4) The PLC opens the oil inlet electromagnetic valves YA91 of the two side cylinders and the oil inlet electromagnetic valve YA92 of the middle cylinder. The PLC gives the proportional servo valves YD91a, YD91b of the two side cylinders and the proportional servo valve YD92 of the middle cylinder to a minimum closing value.
And step two, the slide block is rotated fast to be rotated slowly.
(1) When the slide block runs to a set slow down position, the PLC gradually reduces the opening size of the proportional servo valve YD82 of the lower cavity of the given slide block until the opening size is reduced to a set slow down opening value according to the set slow down pressurizing speed Vs3 and a descending deceleration curve function.
(2) The PLC keeps turning on N3 constant delivery pump electromagnets, keeps turning on the first proportional electromagnet YAP1 and then gives the opening size X31 of the first proportional pump MP 1.
And step three, slowly rotating the sliding block to press downwards.
(1) The PLC turns off the electromagnet of the constant delivery pump.
(2) The PLC keeps turning on the first proportional solenoid YAP1 and gives the opening size X3 of the first proportional pump MP 1.
(3) And the PLC gradually reduces the opening size of the proportional servo valve of the lower cavity of the given YD82 slide block until the opening size is reduced to a given value of a pressing descending opening according to the set isothermal forging pressing descending set speed Vs4 and a descending speed reduction curve function.
(4) The PLC opens the isothermal forging high-frequency corresponding direction valve YT91, and outputs the opening size X4 of the isothermal forging high-frequency corresponding direction valve YT91 through a closed-loop control algorithm according to the isothermal forging pressing downlink set speed Vs 4.
Step four, releasing pressure after the slide block stops descending or pressure maintaining is finished
And the slide block reaches a descending stop position in a fixed distance mode or maintains the pressure after the slide block is pressurized to a set tonnage in a fixed pressure mode.
(1) The PLC closes the oil inlet electromagnetic valves YA91 of the two side cylinders and the oil inlet electromagnetic valve YA92 of the middle cylinder.
(2) The PLC gradually increases the pressure relief proportional servo valves YD91a and YD91b of the given two-side cylinder according to the f1 pressure relief curve function, and gradually increases the pressure relief proportional servo valve YD92 of the given middle cylinder according to the f2 pressure relief curve function until the pressure relief of the two-side cylinder and the middle cylinder is finished. Meanwhile, the PLC gradually increases the main pipeline pressure relief proportional servo valve YD81 according to the pressure relief relation curve of g3 until the pressure relief of the main pipeline is finished and then the minimum closing value is set.
Step five, returning the slide block:
when the user operates the handle to return to the neutral position after the slide block returns to the return gear position, the PLC opens the electromagnetic valve YA21 for the return stroke of the slide block, and simultaneously opens the electromagnets of the constant displacement pump one by one until the slide block reaches the set return speed, and then the speed is maintained to return to stop.
The f1 pressure relief curve function and the f2 pressure relief curve function quickly increase the opening of the proportional servo valve (can shorten the pressure relief time) when the system is at high pressure, the opening increases slowly (can make the pressure relief stable) along with the reduction of the system pressure, and the opening increases rapidly and quickly (can shorten the pressure relief time) when the system pressure is low, so that the purpose of stable and rapid pressure relief is achieved.
The relation between the fast descending/slow descending/pressing descending speed of the slide block and the opening size of the slide block lower cavity proportional servo valve YD82 is set as the fitting relation of the g4 lower cavity oil discharge.
The above description is only for the preferred embodiment of the present invention, and is not intended to limit the present invention in any way, and all simple modifications, equivalent changes and modifications made to the above embodiment according to the technical spirit of the present invention are within the scope of the technical solution of the present invention.
Claims (9)
1. A hydraulic system for a multi-function forging press, comprising at least:
the oil supply part comprises at least eight independent quantitative supply oil ways and three variable supply oil ways;
the power part comprises three hydraulic cylinders for driving the sliding block to move up and down; the three hydraulic cylinders are respectively a left hydraulic cylinder, a middle hydraulic cylinder and a right hydraulic cylinder, and the middle hydraulic cylinder is positioned in the middle of the left hydraulic cylinder and the right hydraulic cylinder; wherein:
the oil supply part is connected with oil inlets of the two oil inlet pipelines through a main pipeline, and an oil outlet of the oil inlet pipeline A is connected with an oil inlet of the middle hydraulic cylinder through a relay pipeline A; an oil outlet of the oil inlet pipeline B is respectively connected with oil inlets of the left hydraulic cylinder and the right hydraulic cylinder through a relay pipeline B; an isothermal forging high-frequency corresponding directional valve is installed on the oil inlet pipeline A, and a main pipeline pressure relief proportional servo valve is installed on the oil inlet pipeline B; the relay pipeline A is provided with a middle cylinder oil inlet electromagnetic valve, and the relay pipeline B is provided with two side cylinder oil inlet electromagnetic valves; the oil inlet of each hydraulic cylinder is connected with an oil tank through a pressure relief pipeline; a pressure relief proportional servo valve is arranged on the pressure relief pipeline; the oil outlets of the left hydraulic cylinder and the right hydraulic cylinder are connected with a main pipeline through return pipelines, and a slider lower cavity proportional servo valve and a slider return electromagnetic valve are installed on the return pipelines.
2. The hydraulic system of a multi-function forging hydraulic press according to claim 1, wherein each set of metering oil path includes a metering pump set and a motor.
3. The hydraulic system of a multi-function forging hydraulic press according to claim 1, wherein each set of variable oil supply lines includes a proportional pump set and a motor.
4. A control system for a hydraulic multi-function forging press for controlling the operating conditions of a hydraulic system according to any one of claims 1 to 3, comprising at least:
the data acquisition part comprises a displacement sensor for acquiring the position information of the slide block, two side cylinder pressure sensors for acquiring the pressure parameters of the left hydraulic cylinder and the right hydraulic cylinder, and a middle cylinder pressure sensor for acquiring the pressure parameter of the middle hydraulic cylinder;
a control section including:
the process selection module comprises a free forging process module, a precision extrusion process module and an isothermal forging process module;
a data receiving module for reading the position data of the slide block and the pressure parameters of the three hydraulic cylinders;
the first data processing module is used for calculating the real-time speed of the sliding block according to the position data of the sliding block;
and the second data processing module is used for controlling the flow of the output constant delivery pump and the output proportional pump and the flow of the high-frequency corresponding directional valve according to the position data of the slide block and the pressure parameters of the three hydraulic cylinders.
5. A control method of a multifunctional hydraulic forging press, characterized in that the following steps are realized based on the free forging process module of claim 4:
defining the slide descending speed provided by each fixed displacement pump as Vq, the maximum slide descending speed provided by each variable displacement pump as Vp, and the opening size of the proportional pump as Xn, wherein Xn is [0, 100% ];
firstly, quickly descending a sliding block;
starting a fast gear descending, setting a fast descending speed Vf1 and a lower cavity oil discharging given function, and giving the size of an opening of a lower cavity proportional servo valve of a sliding block;
prepare for slow down, according to the set slow down pressurization speed Vs1 and the theoretical formula: vs1 ═ N1 × Vq + X11 × Vp + K1 × X12 × Vp, N1 quantitative pumps were turned on; using a first proportional pump, starting a first proportional electromagnet, and setting the opening size X11 of the first proportional pump; judging whether a second proportional pump is used or not, starting a second proportional electromagnet or not, giving the opening size X12 of the second proportional pump, if the second proportional pump is started, setting K1 to 1, and if the second proportional pump is not started, setting K1 to 0;
secondly, the slide block rotates downwards quickly and is pressurized downwards slowly;
starting slow gear descending, setting a slow descending pressurizing speed Vs1 and a descending deceleration curve function, and gradually reducing the opening size of the proportional servo valve of the lower cavity of the given sliding block until the opening size is reduced to a given value of the slow lower opening;
keeping opening N1 constant delivery pump electromagnets and the first proportional electromagnet, setting the opening size X11 of the first proportional pump, and keeping the state of the second proportional electromagnet and setting the opening size X21 of the second proportional pump;
step three, finishing the descending of the sliding block;
closing the constant delivery pump electromagnet and the proportional electromagnet, and closing the oil inlet electromagnetic valves of the cylinders at the two sides and the oil inlet electromagnetic valve of the middle cylinder;
gradually increasing the pressure relief proportional servo valves of the two side cylinders according to the first pressure relief curve function, and gradually increasing the pressure relief proportional servo valves of the middle cylinder according to the second pressure relief curve function until the pressure relief of the three hydraulic cylinders is completed; meanwhile, the main pipeline pressure relief proportional servo valve is gradually increased according to the third pressure relief relation curve until the minimum closing value is given after the pressure relief of the main pipeline is finished;
step four, returning the slide block;
opening the electromagnetic valve for the return stroke of the slide block, and simultaneously opening the electromagnets of the constant delivery pumps one by one until the slide block reaches the set return stroke speed and then keeping the speed return stroke;
step five, finishing the return stroke of the sliding block or performing subsequent actions;
when the return stroke of the slide block reaches a return stroke stop position, the pressing is finished;
in the return stroke process of the sliding block, if the operating handle descends to a high gear, the first step is skipped;
in the return process of the sliding block, if the operating handle descends to a slow gear, the sliding block descends slowly, the constant delivery pumps are started to N1 one by one according to the set slow descending pressurizing speed Vs1, the first proportional electromagnet is started, the opening size X11 of the first proportional pump is given, whether the second proportional electromagnet is started or not is judged, and after the opening size X21 of the second proportional pump is given or not, the oil inlet electromagnetic valves of the two cylinders and the oil inlet electromagnetic valve of the middle cylinder are started; setting the two side cylinder pressure relief proportional servo valves and the middle cylinder pressure relief proportional servo valve as a minimum closing value; and skipping to the third step.
6. A control method of a multifunctional hydraulic forging press is characterized in that the following steps are realized based on the precision extrusion process module of claim 4:
defining the slide descending speed provided by each fixed displacement pump as Vq, the maximum slide descending speed provided by each variable displacement pump as Vp, and the opening size of the proportional pump as Xn, wherein Xn is [0, 100% ];
firstly, quickly descending a sliding block;
starting any one of fast gear descending or slow gear descending, setting a fast descending speed Vf2 and a lower cavity oil discharge given function, and giving the opening size of a sliding block lower cavity proportional servo valve;
prepare for slow down, set the slow down pressurization speed Vs2 and the theoretical equation: vs2 ═ N2 × Vq + X21 × Vp + K1 × X22 × Vp, N2 quantitative pumps were turned on; using a first proportional pump, starting a first proportional electromagnet and setting the opening size X21 of the first proportional pump; judging whether a second proportional pump is used or not, starting a second proportional electromagnet or not, setting the opening size X22 of the second proportional pump, and if the second proportional pump is started, K1 is equal to 1, and if the second proportional pump is not started, K1 is equal to 0;
the three hydraulic cylinders move downwards, negative pressure is generated in the upper cavities of the three hydraulic cylinders, and the liquid filling valve is passively opened for liquid filling;
opening oil inlet electromagnetic valves of the two side cylinders and an oil inlet electromagnetic valve of the middle cylinder, and setting the pressure relief proportional servo valves of the two side cylinders and the pressure relief proportional servo valve of the middle cylinder as a minimum closing value;
secondly, the slide block rotates downwards quickly and is pressurized downwards slowly;
the slide block moves to a set slow down position, and the opening size of the proportional servo valve of the lower cavity of the given slide block is gradually reduced until the opening size is reduced to a given value of the slow down opening according to a set slow down pressurizing speed Vs2 and a descending deceleration curve function;
keeping opening N2 constant delivery pump electromagnets, keeping opening the first proportional electromagnet, performing closed-loop correction on the basis of a theoretical value X11, then setting the opening size X211 of the first proportional pump, and keeping the state of the second proportional electromagnet and the opening size X22 of the second proportional pump;
step three, the pressure is released after the sliding block stops descending or the pressure maintaining is finished;
closing the constant delivery pump electromagnet and the proportional electromagnet, and closing the oil inlet electromagnetic valves of the cylinders at the two sides and the oil inlet electromagnetic valve of the middle cylinder;
gradually increasing the pressure relief proportional servo valves of the two side cylinders according to the first pressure relief curve function, and gradually increasing the pressure relief proportional servo valves of the middle cylinder according to the second pressure relief curve function until the pressure relief of the three hydraulic cylinders is completed; meanwhile, the main pipeline pressure relief proportional servo valve is gradually increased according to a third pressure relief relation curve until the main pipeline pressure relief is finished and then a minimum closing value is set;
step four, returning the slide block;
and after the operating handle is shifted to the return stroke gear of the sliding block, the operating handle is reset to a neutral position, the electromagnetic valve for return stroke of the sliding block is opened, and meanwhile, the electromagnets of the constant delivery pump are opened one by one until the sliding block reaches the set return stroke speed, and the speed return stroke is kept until the sliding block stops.
7. A control method of a multifunctional hydraulic forging press is characterized in that the following steps are realized based on the isothermal forging process module of claim 4:
defining the slide descending speed provided by each fixed displacement pump as Vq, the maximum slide descending speed provided by each variable displacement pump as Vp, and the opening size of the proportional pump as Xn, wherein Xn is [0, 100% ];
firstly, quickly descending a sliding block;
starting any one of fast gear descending or slow gear descending, setting a fast descending speed Vf2 and a lower cavity oil discharge given function, and giving the opening size of a sliding block lower cavity proportional servo valve;
prepare for slow down, according to the set slow down pressurization speed Vs3 and the theoretical formula: when Vs3 is N3 × Vq + X23 × Vp, N3 quantitative pumps are started; using a first proportional pump, starting a first proportional electromagnet, and setting the opening size X31 of the first proportional pump;
the three hydraulic cylinders move downwards, negative pressure is generated in the upper cavities of the three hydraulic cylinders, and the liquid filling valve is passively opened for liquid filling;
opening oil inlet electromagnetic valves of the two side cylinders and an oil inlet electromagnetic valve of the middle cylinder, and setting the pressure relief proportional servo valves of the two side cylinders and the pressure relief proportional servo valve of the middle cylinder as a minimum closing value;
step two, the slide block is rotated from fast downward to slow downward;
the slide block moves to a set slow down position, and the opening size of the proportional servo valve of the lower cavity of the given slide block is gradually reduced until the opening size is reduced to a given value of the slow down opening according to a set slow down pressurizing speed Vs3 and a descending deceleration curve function;
keeping opening N3 constant delivery pump electromagnets, keeping opening a first proportional electromagnet, and setting the opening size X31 of the first proportional pump;
step three, slowly rotating the sliding block to press downwards;
closing the electromagnet of the constant delivery pump;
keeping turning on the first proportional electromagnet, and setting the opening size X3 of the first proportional pump MP 1;
gradually reducing the opening size of the proportional servo valve of the lower cavity of the given slide block until the opening size is reduced to a given value of a pressing descending opening according to a set isothermal forging pressing descending set speed Vs4 and a descending deceleration curve function;
opening the isothermal forging high-frequency corresponding direction valve, outputting the opening size X4 of the isothermal forging high-frequency corresponding direction valve according to the isothermal forging pressing descending set speed Vs4 through a closed-loop control algorithm;
step four, the pressure is released after the sliding block stops descending or the pressure maintaining is finished;
closing the oil inlet electromagnetic valves of the two side cylinders and the oil inlet electromagnetic valve of the middle cylinder;
gradually increasing the pressure relief proportional servo valves of the two side cylinders according to the first pressure relief curve function, and gradually increasing the pressure relief proportional servo valves of the middle cylinder according to the second pressure relief curve function until the pressure relief of the three hydraulic cylinders is completed; meanwhile, the main pipeline pressure relief proportional servo valve is gradually increased according to a third pressure relief relation curve until the main pipeline pressure relief is finished and then a minimum closing value is set;
step five, returning the slide block;
and when the operating handle is shifted to the return stroke position of the sliding block, the operating handle is reset to a neutral position, the electromagnetic valves for return stroke of the sliding block are opened, and meanwhile, the electromagnets of the constant delivery pump are opened one by one until the sliding block reaches the set return stroke speed, and the speed return stroke is kept until the sliding block stops.
8. The control method of the hydraulic multi-function forging press according to any one of claims 5 to 7, wherein the pressure of the two-side cylinder pressure sensor as a function of the opening of the two-side cylinder pressure relief proportional servo valve follows the following relationship:
wherein p0, p1, p2, p3, p4, p5, a1, a2, A3, a4, a5, K11, K12, K13, K14, K15, and K16 are constants taken in debugging;
the relation function of the pressure of the middle cylinder pressure sensor and the opening of the middle cylinder pressure relief proportional servo valve follows the following relation:
wherein pb0, pb1, pb2, pb3, pb4, pb5, B1, B2, B3, B4, B5, K21, K22, K23, K24, K25, and K26 are constants taken in debugging;
when the hydraulic system is at a high pressure, the opening of the pressure relief proportional servo valve is rapidly increased, the opening is increased in speed to be slowly increased along with the reduction of the pressure, and when the hydraulic system is at a low pressure, the opening of the pressure relief proportional servo valve is rapidly increased.
9. The control method of the multifunctional hydraulic forging press according to any one of claims 5 to 7, wherein in the first to fourth steps, the relationship between the slide block fast descent/slow descent/pressing descent speed and the opening size of the proportional servo valve in the lower cavity of the slide block is set to fit the oil discharge in the lower cavity.
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| CN110126342A (en) * | 2019-05-17 | 2019-08-16 | 天津市天锻压力机有限公司 | The process control system and control method of semicontinuous electrode hydraulic press |
| WO2021022682A1 (en) * | 2019-08-06 | 2021-02-11 | 南通锻压设备如皋有限公司 | Method for combined control of speed and pressure of orbital hydraulic press |
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107052210A (en) * | 2017-04-26 | 2017-08-18 | 天津市天锻压力机有限公司 | The constant strain control system and control method of Superplastic Isothermal Forging hydraulic press |
| CN107120328A (en) * | 2017-04-26 | 2017-09-01 | 天津市天锻压力机有限公司 | The process control system and control method of isothermal forging hydropress |
| CN108687283A (en) * | 2018-03-30 | 2018-10-23 | 天津市天锻压力机有限公司 | A kind of electrohydraulic control system and technological forming method being hot extruded into type hydraulic machine |
| CN110126342A (en) * | 2019-05-17 | 2019-08-16 | 天津市天锻压力机有限公司 | The process control system and control method of semicontinuous electrode hydraulic press |
| WO2021022682A1 (en) * | 2019-08-06 | 2021-02-11 | 南通锻压设备如皋有限公司 | Method for combined control of speed and pressure of orbital hydraulic press |
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