CN110328244B - Hydraulic tension system of straight pull type cold/warm rolling experiment machine and control method thereof - Google Patents

Hydraulic tension system of straight pull type cold/warm rolling experiment machine and control method thereof Download PDF

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Publication number
CN110328244B
CN110328244B CN201910612933.9A CN201910612933A CN110328244B CN 110328244 B CN110328244 B CN 110328244B CN 201910612933 A CN201910612933 A CN 201910612933A CN 110328244 B CN110328244 B CN 110328244B
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tension
valve
oil
pressure reducing
oil cylinder
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CN110328244A (en
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王贵桥
孙涛
李建平
牛文勇
花福安
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Northeastern University China
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Northeastern University China
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Priority to PCT/CN2019/096263 priority patent/WO2021003761A1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/48—Tension control; Compression control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • 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
    • 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
    • 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
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Abstract

A hydraulic tension system of a straight pull type cold/warm rolling experiment machine and a control method thereof belong to the technical field of hydraulic control, and comprise a constant pressure oil source system, a left tension control unit, a right tension control unit, a large-specification left tension oil cylinder internally provided with a first displacement sensor, a small-specification left tension oil cylinder internally provided with a second displacement sensor, a large-specification right tension oil cylinder internally provided with a third displacement sensor and a small-specification right tension oil cylinder internally provided with a fourth displacement sensor. The tension oil cylinder with large and small specifications has the same mechanical connection size and oil port size and is convenient to replace. The three-way proportional pressure reducing valve with large flow and large pressure adjusting range is used for controlling the large-specification tension oil cylinder, so that the control requirement of large tension is met; the three-way proportional pressure reducing valve with small flow and small pressure adjusting range is used for controlling the low-friction damping small-specification tension oil cylinder, and high-precision small-tension control is facilitated.

Description

Hydraulic tension system of straight pull type cold/warm rolling experiment machine and control method thereof
Technical Field
The invention belongs to the technical field of hydraulic control, and particularly relates to a hydraulic tension system and a control method thereof, which are suitable for a straight-pull cold/warm rolling experiment machine with consideration of the requirements of large and small tension control.
Background
The straight-pull cold/warm experimental machine is mainly used for cold machining and warm machining of automobile plates, electrical steel, high-strength steel, fine-blanking steel, titanium, magnesium-based alloy and other materials difficult to deform, and is important pilot test research equipment for researching special rolling process performance of metal materials and developing products. Strip tension control is a very important core technology for different metal strips during the cold and warm rolling process from a billet to a very thin strip product. There are many factors affecting the tension control accuracy, including time-varying property of the controlled object during rolling, nonlinearity, and strong coupling between left and right tension, and it is very difficult to achieve high-accuracy tension control. The control difficulty is very high in consideration of the characteristics of position disturbance, strong coupling and time-varying property of redundant force in the cold rolling tension control process.
In order to meet the requirement of constant tension rolling and realize high-precision tension control, the technical personnel in the field disclose an invention patent of a hydraulic tension control system and a method of a straight pull type cold rolling experimental machine, and the patent application number is 201510105358.5. The invention researches the defects of the prior art, realizes high-precision tension control by presetting the control quantity of the servo valve and combining the pressure control of the proportional overflow valve, and enhances the robustness of the tension control system. In the method, a servo valve is in an open-loop control mode in the rolling process, the opening degree of the servo valve is calculated through a flow formula of the servo valve, and key parameters of the formula are measured by a servo valve manufacturer on a new valve under the conditions of specific system working pressure, oil viscosity and oil temperature. When the servo valve works, the actual working pressure of the system, the viscosity of oil and the temperature of the oil are in a dynamic change process, and the dynamic difference inevitably exists between the actual working pressure of the system, the actual viscosity of the oil and the actual temperature of the oil and the test state of a manufacturer, and the difference can cause the calculation of the flow formula to generate dynamic deviation, so that the tension control precision is influenced. In addition, with the continuous abrasion of the working edge of the servo valve, the calculation deviation of the flow formula is larger and larger, so that the final tension control precision is influenced. In addition, in the process of stopping the vehicle, the tension oil cylinder at the inlet side can generate overshoot due to inertia, so that the tension at the inlet side is smaller than a set value, and because the proportional overflow valve belongs to an overflow working mode, when the tension is smaller, the closed-loop adjustment of the proportional overflow valve is ineffective, and certain tension fluctuation can be generated during the next pass switching. The above-mentioned influence is negligible for large tension control, but causes great trouble for micro tension control.
The invention patent of a hydraulic tension warm rolling mill micro-tension control system and method is disclosed by the technical personnel in the field, and the patent application number is 201510179687.4. The proportional pressure reducing valve is arranged at a high-pressure inlet of the servo valve, and the proportional overflow valve is arranged at an outlet of the servo valve (namely a rod cavity of the tension cylinder). In the rolling process, a servo valve on the outlet side is in an open state (the controlled quantity is 70-100%), and the tension of the servo valve is subjected to closed-loop control through a proportional pressure reducing valve on the outlet side; the inlet-side servo valve is in a closed state, and the tension of the inlet-side servo valve is closed-loop controlled by the inlet-side proportional relief valve. Since the rolling mill operates in a reversible reciprocating rolling manner, the inlet side and the outlet side of the previous pass are respectively changed to the outlet side and the inlet side in the next pass. Tension control right connection processes of the proportional pressure reducing valve and the proportional overflow valve and switching processes of opening and closing of the servo valve exist between adjacent passes, the two processes have obvious influence on tension control precision and influence rolling rhythm at the same time.
With the continuous promotion of material processing technology research and development, higher requirements are put forward on process equipment of a cold/warm rolling experiment machine, and the requirements for stable control of large tension of steel material thick strip rolling and stable control of micro tension of non-ferrous metal ultrathin strip such as magnesium alloy and the like are met. The large-size tension oil cylinder is required to be adopted due to the requirement of large tension, and the large-size tension oil cylinder has larger friction even if a low-friction damping design is adopted, and the friction is even far larger than the tension limit which can be borne by the ultrathin nonferrous metal rolled piece. Because the friction force has the typical non-linear characteristic, the direction and the magnitude of the friction force have uncertainty particularly in a static friction force state. It can be seen that none of the prior art is suitable for both large tension control and small and even micro tension control. Therefore, a new design of hydraulic tension control system is needed to meet the research and development requirements of the process.
Disclosure of Invention
Aiming at the problems in the prior art and the control requirement of considering both large tension and small tension, the invention provides the hydraulic tension system of the straight-pull cold/warm rolling experiment machine and the control method thereof, which can meet the tension control requirement of large span and have simple and reliable control method.
In order to achieve the purpose, the invention adopts the following technical scheme:
a hydraulic tension system of a straight pull type cold/warm rolling experiment machine comprises a constant pressure oil source system, a left hydraulic clamp, a right hydraulic clamp, a left tension oil cylinder, a right tension oil cylinder, a left tension control unit and a right tension control unit, wherein the left hydraulic clamp is connected with a piston rod of the left tension oil cylinder, a left tensiometer is arranged at the joint of the left hydraulic clamp and the left tension oil cylinder, the right hydraulic clamp is connected with a piston rod of the right tension oil cylinder, a right tensiometer is arranged at the joint of the right hydraulic clamp and the right tension oil cylinder, a rolled piece is clamped between the left hydraulic clamp and the right hydraulic clamp, the rolled piece is rolled back and forth by a rolling mill when being applied with tension by the left tension oil cylinder and the right tension oil cylinder, a high pressure oil outlet of the constant pressure oil source system is respectively communicated with a high pressure oil inlet of the left tension control unit and a high pressure inlet of the right, the back pressure oil outlet of the constant pressure oil source system is communicated with the back pressure oil inlet of the left tension control unit, the oil return port of the constant pressure oil source system is respectively communicated with the oil return port of the left tension control unit and the oil return port of the right tension control unit, and the back pressure oil outlet of the left tension control unit is communicated with the back pressure oil inlet of the right tension control unit.
The left tension control unit comprises a first filter, a first one-way valve, a first pressure reducing valve, a second one-way valve, a first three-way proportional pressure reducing valve, a first electromagnetic directional valve, a second three-way proportional pressure reducing valve, a first hydraulic control one-way valve, a second hydraulic control one-way valve, a first energy accumulator, a third one-way valve, a second electromagnetic directional valve, a third electromagnetic directional valve, a first stop valve, a second stop valve, a first oil pressure sensor, a second oil pressure sensor and a first pressure gauge; the high-pressure oil inlet of the left tension control unit is communicated with the inlet of a first filter, the outlet of the first filter is communicated with the inlet of a first one-way valve, the outlet of the first one-way valve is respectively communicated with the inlet of a first three-way proportional pressure reducing valve, the inlet of a first electromagnetic directional valve and the inlet of the first pressure reducing valve, the outlet of the first pressure reducing valve is respectively communicated with the inlet of a second three-way proportional pressure reducing valve, a first energy accumulator and a first pressure gauge, the oil discharge port of the first three-way proportional pressure reducing valve is respectively communicated with the outlet of the second one-way valve, the oil discharge port of the second three-way proportional pressure reducing valve, the oil discharge port of the first pressure reducing valve, the oil return port of a third electromagnetic directional valve and the inlet of the third one-way valve, the inlet of the second one-way valve is communicated with the oil return port of the first electromagnetic directional valve, the control oil return port, a second working oil port of the first electromagnetic directional valve is communicated with a control oil port of a second hydraulic control one-way valve, an inlet of the second hydraulic control one-way valve is communicated with an outlet of a second three-way proportional pressure reducing valve, an inlet of the first hydraulic control one-way valve is respectively communicated with an outlet of the second hydraulic control one-way valve and an inlet of a third electromagnetic directional valve, an oil return port of the second electromagnetic directional valve is communicated with an outlet of the third one-way valve and an oil return port of the left tension control unit, an inlet of the second electromagnetic directional valve is communicated with a back pressure oil inlet of the left tension control unit, a first working oil port of the second electromagnetic directional valve is respectively communicated with a back pressure oil outlet of the left tension control unit, a first oil pressure sensor and an inlet of a first stop valve, an outlet of the first stop valve is communicated with a first working oil port of the left tension control unit, and a first working oil port of the third electromagnetic directional valve is respectively communicated with an inlet of the second, the outlet of the second stop valve is communicated with a second working oil port of the left tension control unit, a first working oil port of the left tension control unit is communicated with a rodless cavity of the left tension oil cylinder, and a second working oil port of the left tension control unit is communicated with a rod cavity of the left tension oil cylinder.
The right tension control unit comprises a second filter, a fourth one-way valve, a second pressure reducing valve, a fifth one-way valve, a third three-way proportional pressure reducing valve, a fourth electromagnetic directional valve, a fourth three-way proportional pressure reducing valve, a third hydraulic control one-way valve, a fourth hydraulic control one-way valve, a second energy accumulator, a sixth one-way valve, a fifth electromagnetic directional valve, a third stop valve, a fourth stop valve, a third oil pressure sensor, a fourth oil pressure sensor and a second pressure gauge; the high-pressure oil inlet of the right tension control unit is communicated with the inlet of a second filter, the outlet of the second filter is communicated with the inlet of a fourth one-way valve, the outlet of the fourth one-way valve is respectively communicated with the inlet of a third three-way proportional pressure reducing valve, the inlet of a fourth electromagnetic directional valve and the inlet of a second pressure reducing valve, the outlet of the second pressure reducing valve is respectively communicated with the inlet of the fourth three-way proportional pressure reducing valve, a second energy accumulator and a second pressure gauge, the oil discharge port of the third three-way proportional pressure reducing valve is communicated with the outlet of a fifth one-way valve, the oil discharge port of the fourth three-way proportional pressure reducing valve, the oil discharge port of the second pressure reducing valve, the oil return port of the fifth electromagnetic directional valve and the inlet of a sixth one-way valve, the inlet of the fifth one-way valve is communicated with the oil return port of the fourth electromagnetic directional valve, the outlet of the third three-way proportional pressure reducing valve is communicated with the outlet of the third hydraulic control, a second working oil port of the fourth electromagnetic directional valve is communicated with a control oil port of the fourth hydraulic control one-way valve, an inlet of the fourth hydraulic control one-way valve is communicated with an outlet of a fourth three-way proportional pressure reducing valve, an inlet of the third hydraulic control one-way valve is communicated with an outlet of the fourth hydraulic control one-way valve and an inlet of a fifth electromagnetic directional valve, an outlet of the sixth one-way valve is communicated with an oil return port of the right tension control unit, a first working oil port of the fifth electromagnetic directional valve is respectively communicated with an inlet of a third oil pressure sensor and an inlet of a third stop valve, an outlet of the third stop valve is communicated with a first working oil port of the right tension control unit, a back pressure oil inlet of the right tension control unit is communicated with the fourth oil pressure sensor and an inlet of the fourth stop valve, an outlet of the fourth stop valve is communicated with a second working oil port of the right tension control unit, a first working oil port of the right tension control unit is communicated, and a second working oil port of the right tension control unit is communicated with a rodless cavity of the right tension oil cylinder.
The left tension oil cylinder comprises a large-specification left tension oil cylinder and a small-specification left tension oil cylinder, a first shift sensor is arranged in the large-specification left tension oil cylinder, a second shift sensor is arranged in the small-specification left tension oil cylinder, and the external connection size and the oil port size of the large-specification left tension oil cylinder are the same as those of the small-specification left tension oil cylinder.
The right tension oil cylinder comprises a large-specification right tension oil cylinder and a small-specification right tension oil cylinder, a third displacement sensor is arranged in the large-specification right tension oil cylinder, a fourth displacement sensor is arranged in the small-specification right tension oil cylinder, and the external connection size and the oil port size of the large-specification right tension oil cylinder are the same as those of the small-specification right tension oil cylinder.
The large-specification left tension oil cylinder and the large-specification right tension oil cylinder are the same in model, and the small-specification left tension oil cylinder and the small-specification right tension oil cylinder are the same in model.
When the steel material is rolled under high tension of 4-50kN, a first working oil port of the left tension control unit is communicated with a rodless cavity of the large-specification left tension oil cylinder, a second working oil port of the left tension control unit is communicated with a rod cavity of the large-specification left tension oil cylinder, a first working oil port of the right tension control unit is communicated with a rod cavity of the large-specification right tension oil cylinder, and a second working oil port of the right tension control unit is communicated with a rodless cavity of the large-specification right tension oil cylinder.
When the magnesium alloy material is rolled under the small tension of 0.5-4kN, a first working oil port of the left tension control unit is communicated with a rodless cavity of the small-specification left tension oil cylinder, a second working oil port of the left tension control unit is communicated with a rod cavity of the small-specification left tension oil cylinder, a first working oil port of the right tension control unit is communicated with a rod cavity of the small-specification right tension oil cylinder, and a second working oil port of the right tension control unit is communicated with the rodless cavity of the small-specification right tension oil cylinder.
The first energy accumulator and the second energy accumulator both adopt leather bag type energy accumulators, and the first three-way proportional pressure reducing valve and the third three-way proportional pressure reducing valve have the same model; the second three-way proportional pressure reducing valve and the fourth three-way proportional pressure reducing valve have the same model.
A control method of hydraulic tension of a straight-pull cold/warm rolling experiment machine adopts a hydraulic tension system of the straight-pull cold/warm rolling experiment machine, and comprises the following steps:
step 1: before the system operates for the first time, a nitrogen cylinder is used for filling nitrogen into the first energy accumulator, and the nitrogen filling pressure is 0.75 time of the set pressure of the first pressure reducing valve; filling nitrogen into the second energy accumulator through a nitrogen cylinder, wherein the nitrogen filling pressure is 0.75 times of the set pressure of the second pressure reducing valve;
step 2: starting the constant-pressure oil source system, and adjusting the set pressure of the first pressure reducing valve to be 1-3MPa higher than the rated adjusting pressure of the second three-way proportional pressure reducing valve; the set pressure of the second pressure reducing valve is regulated to be 1-3MPa higher than the rated regulation pressure of the fourth three-way proportional pressure reducing valve;
and step 3: selecting the specification of a tension oil cylinder according to the requirements of a rolling process, namely selecting a large-specification left tension oil cylinder and a large-specification right tension oil cylinder to perform tension loading on a rolled piece when a steel material is rolled at a high tension of 4-50 kN; when the magnesium alloy material is rolled with small tension of 0.5-4kN, a small-specification left tension oil cylinder and a small-specification right tension oil cylinder are selected to carry out tension loading on a rolled piece; marking the left tension oil cylinder in a working state as C1, and marking the right tension oil cylinder in a working state as C2; if the tension oil cylinders communicated with the left tension control unit and the right tension control unit are not consistent with the required oil cylinders at present, the constant-pressure oil source system needs to be closed, after the pressures measured by the first oil pressure sensor, the second oil pressure sensor, the third oil pressure sensor and the fourth oil pressure sensor are all returned to zero, the first stop valve, the second stop valve, the third stop valve and the fourth stop valve are all closed, the tension oil cylinders are replaced, the first stop valve, the second stop valve, the third stop valve and the fourth stop valve are all opened after the replacement is finished, and then the constant-pressure oil source system is started; then, according to the process selection result, determining the current working mode or state of each valve group: when rolling with large tension of 4-50kN is carried out, the control signals of the second three-way proportional pressure reducing valve and the fourth three-way proportional pressure reducing valve are 0% of the rated signal of the valve, the control signals of the first three-way proportional pressure reducing valve and the third three-way proportional pressure reducing valve are 20% -30% of the rated signal of the valve, and the electromagnet DT2 of the first electromagnetic reversing valve and the electromagnet DT4 of the fourth electromagnetic reversing valve are controlled to be powered; when the rolling is carried out under the low tension of 0.5-4kN, the control signals of the first three-way proportional pressure reducing valve and the third three-way proportional pressure reducing valve are 80% of the rated signal of the valve, and the control signals of the second three-way proportional pressure reducing valve and the fourth three-way proportional pressure reducing valve are 30% -40% of the rated signal of the valve; marking a first three-way proportional pressure reducing valve and a third three-way proportional pressure reducing valve for closed-loop tension control as V1 and V2, or marking a second three-way proportional pressure reducing valve and a fourth three-way proportional pressure reducing valve for closed-loop tension control as V1 and V2, and controlling an electromagnet DT1 of the first electromagnetic directional valve and an electromagnet DT3 of the fourth electromagnetic directional valve to be electrified;
and 4, step 4: controlling an electromagnet DT6 of the second electromagnetic directional valve to be electrified so as to lead the rodless cavities of the two tension oil cylinders to be communicated with the back pressure oil; the extending, retracting and stopping actions of the large-specification left tension oil cylinder or the small-specification left tension oil cylinder can be respectively realized by inching and controlling the power on or power off of the two electromagnets DT7 and DT8 of the third electromagnetic reversing valve; the stretching, retracting and stopping actions of the large-specification right tension oil cylinder or the small-specification right tension oil cylinder can be respectively realized by inching and controlling the power on or power off of two electromagnets DT9 and DT10 of the fifth electromagnetic reversing valve; thereby completing the clamping work of the rolled piece;
and 5: controlling the roll gap to the first secondary roll gap through a roll gap control system of the rolling mill; then, tension of the rolled piece is established, and the tension of the rolled piece is established in two ways:
(1) keeping the power-on state of an electromagnet DT6 of the second electromagnetic reversing valve, controlling the electromagnet DT8 of the third electromagnetic reversing valve and the electromagnet DT10 of the fifth electromagnetic reversing valve to be powered on with a marked variable By of 1, putting a three-way proportional pressure reducing valve marked as V1 and a left tensiometer into left tension closed-loop control, putting the three-way proportional pressure reducing valve marked as V2 and the right tensiometer into right tension closed-loop control, and establishing outlet tension and inlet tension for the rolled piece according to a tension rule;
(2) controlling an electromagnet DT5 of the second electromagnetic reversing valve to be electrified, controlling an electromagnet DT8 of the third electromagnetic reversing valve and an electromagnet DT10 of the fifth electromagnetic reversing valve to be electrified, simultaneously putting a V1 three-way proportional pressure reducing valve and a left tensiometer which are marked as V1 into left tension closed-loop control, putting the V2 three-way proportional pressure reducing valve and the right tensiometer into right tension closed-loop control, and establishing outlet tension and inlet tension for the rolled piece according to a tension rule;
step 6: reversible cold or warm rolling is carried out on the rolled piece according to the rolling schedule;
and 7: after the rolling is finished, the rolling mill is in a stop state, the tension of the outlet and inlet of a rolled piece is adjusted to be zero through the tension closed-loop control in the step five, the electromagnets DT8 of the third electromagnetic directional valve and the electromagnets DT10 of the fifth electromagnetic directional valve are controlled to be powered off, and the control signals of the two three-way proportional pressure reducing valves marked as V1 and V2 are restored to the numerical values determined in the step three; if the variable By set in the step 5 is 1, directly entering a step 8; if the variable By set in the step 5 is 0, controlling the electromagnet DT6 of the second electromagnetic directional valve to be electrified;
and 8: and opening the left hydraulic clamp, controlling the two tension oil cylinders marked as C1 and C2 to retract, opening the right hydraulic clamp, taking down the rolled piece, setting the electromagnet states of all the electromagnetic directional valves to zero, setting all three-way proportional pressure reducing valve control signals to zero, and ending the experiment.
In the above description, when it is required to control a certain electromagnet of a certain electromagnetic directional valve to be powered on, another electromagnet of the same valve is controlled to be powered off by default.
The invention has the beneficial effects that:
(1) the tension oil cylinder with large and small specifications has the same mechanical connection size and oil port size and is convenient to replace. The three-way proportional pressure reducing valve with large flow and large pressure adjusting range is used for controlling the large-specification tension oil cylinder, so that the control requirement of large tension is met; the three-way proportional pressure reducing valve with small flow and small pressure adjusting range is used for controlling the low-friction damping small-specification tension oil cylinder, and high-precision small-tension control is facilitated.
(2) Except that the replacement of large and small specification tension oil cylinders requires mechanical operation, the large and small tension control modes can realize one-key type on-line switching, and are convenient and reliable.
(3) When the pressure at the load end is lower than the set pressure of the three-way proportional pressure reducing valve, the three-way proportional pressure reducing valve has a pressure reducing function; when the pressure at the load end is higher than the set pressure of the three-way proportional pressure reducing valve, the three-way proportional pressure reducing valve has an overflow function; therefore, in the whole rolling process, the tension closed-loop control right is always shared by the two three-way proportional pressure reducing valves marked as V1 and V2, only two tension closed-loop controls are adopted, compared with the prior art, the control logic is simple and reliable, and the problem of tension fluctuation caused by the control right switching process does not exist.
(4) The third electromagnetic directional valve and the fifth electromagnetic directional valve do not participate in tension closed-loop control, so after the two servo valves in the prior art are replaced by the third electromagnetic directional valve and the fifth electromagnetic directional valve, the cost is saved, the requirement of the system on the cleanliness of oil is reduced, and all problems caused by open-loop feedforward by utilizing the servo valves in the prior art are solved. Although a certain tension oil cylinder position control precision is lost, the position control mode of the tension oil cylinder is only used for loading and unloading rolled pieces, so that the loss is not important.
(5) The first pressure reducing valve and the second pressure reducing valve are arranged in front of the second three-way proportional pressure reducing valve and the fourth three-way proportional pressure reducing valve respectively, and the inlets of the two three-way proportional pressure reducing valves are subjected to pressure reduction, so that the tension adjusting process in a small tension control mode is more stable, and high-precision small tension control is facilitated.
(6) From the establishment of the tension of the rolled piece to the completion of the whole rolling process, the rodless cavities of the two tension oil cylinders are communicated with the oil return box by controlling the DT5 of the second electromagnetic directional valve to be electrified, so that the backpressure of the rodless cavities is zero, and the interference of the oil pressure fluctuation of the rodless cavities of the tension oil cylinders on the tension can be completely eliminated.
(7) In the experiment process, the experiment needs to be stopped under any special condition, all the electromagnet states of all the electromagnetic directional valves can be set to zero, the position locking of the two tension oil cylinders can be realized, and the experiment safety is improved.
Drawings
FIG. 1 is a schematic diagram of a hydraulic tension system of a straight pull cold/warm rolling test machine according to the present invention;
FIG. 2 is a front view of the appearance and connection dimension of the large-sized tension cylinder in the embodiment;
FIG. 3 is a top view of the shape and connection dimensions of a large-sized tension cylinder in the embodiment;
FIG. 4 is a sectional view of the large-sized tension cylinder A-A in the embodiment;
FIG. 5 is a front view of the shape and connection dimensions of a small-sized tension cylinder in the embodiment;
FIG. 6 is a top view of the small-sized tension cylinder in the embodiment;
FIG. 7 is a sectional view of the small-sized tension cylinder B-B in the embodiment;
in the figure, I is a left tension control unit, and II is a right tension control unit; 1-a first filter, 2-a first check valve, 3-a first pressure reducing valve, 4-a second check valve, 5-a first three-way proportional pressure reducing valve, 6-a first electromagnetic directional valve, 7-a second three-way proportional pressure reducing valve, 8-a first pilot operated check valve, 9-a second pilot operated check valve, 10-a first accumulator, 11-a third check valve, 12-a second electromagnetic directional valve, 13-a third electromagnetic directional valve, 14-a first stop valve, 15-a second stop valve, 16-a first oil pressure sensor, 17-a second oil pressure sensor, 18.1-a first displacement sensor, 19.1-a large-specification left tension cylinder, 18.2-a second displacement sensor, 19.2-a small-specification left tension cylinder, 20-a second filter, 21-a fourth check valve, 22-a second pressure reducing valve, 23-a fifth check valve, 24-a third three-way proportional pressure reducing valve, 25-a fourth electromagnetic directional valve, 26-a fourth three-way proportional pressure reducing valve, 27-a third hydraulic control one-way valve, 28-a fourth hydraulic control one-way valve, 29-a second accumulator, 30-a sixth one-way valve, 31-a fifth electromagnetic directional valve, 32-a third cut-off valve, 33-a fourth cut-off valve, 34-a third oil pressure sensor, 35-a fourth oil pressure sensor, 36.1-a third displacement sensor, 37.1-a large specification right tension oil cylinder, 36.2-a fourth displacement sensor, 37.2-a small specification right tension oil cylinder, 38-a first pressure gauge, 39-a second pressure gauge, 40-a left tensiometer, 41-a left hydraulic clamp, 42-a right tensiometer, 43-a right hydraulic clamp, 44-a rolling mill and 45-a constant pressure oil source system;
ps-a high-pressure oil outlet of the constant-pressure oil source system, T-a return port of the constant-pressure oil source system, P0-a back-pressure oil outlet of the constant-pressure oil source system, K11-a high-pressure oil inlet of the left tension control unit, K12-a back-pressure oil inlet of the left tension control unit, K13-a back-pressure oil outlet of the left tension control unit, K14-a return port of the left tension control unit, K15-a first working port of the left tension control unit, K16-a second working port of the left tension control unit, K21-a high-pressure oil inlet of the right tension control unit, K22-a back-pressure oil inlet of the right tension control unit, K23-a return port of the right tension control unit, K24-a first working port of the right tension control unit, K25-a second working port of the right tension control unit, a 1-an inlet of the first filter, B1-an outlet of the first filter, a 2-an inlet of the first check valve, and B2-an outlet of the first check valve, p3-the inlet of the first pressure reducing valve, A3-the outlet of the first pressure reducing valve, T3-the oil discharge port of the first pressure reducing valve, A4-the inlet of the second check valve, B4-the outlet of the second check valve, P5-the inlet of the first three-way proportional pressure reducing valve, A5-the outlet of the first three-way proportional pressure reducing valve, T5-the oil discharge port of the first three-way proportional pressure reducing valve, P6-the inlet of the first electromagnetic directional valve, T6-the oil return port of the first electromagnetic directional valve, A6-the first working oil port of the first electromagnetic directional valve, B6-the second working oil port of the first electromagnetic directional valve, P7-the inlet of the second three-way proportional pressure reducing valve, A7-the outlet of the second three-way proportional pressure reducing valve, T7-the oil discharge port of the second three-way proportional pressure reducing valve, A8-the inlet of the first check valve, B8-the outlet of the first pilot-controlled check valve, X8-the control port of the first check valve, A9-the second pilot controlled hydraulic, b9-an outlet of the second hydraulic check valve, X9-a control oil port of the second hydraulic check valve, a 11-an inlet of the third check valve, B11-an outlet of the third check valve, P12-an inlet of the second electromagnetic directional valve, T12-an oil return port of the second electromagnetic directional valve, a 12-a first working oil port of the second electromagnetic directional valve, B12-a second working oil port of the second electromagnetic directional valve, P13-an inlet of the third electromagnetic directional valve, T13-an oil return port of the third electromagnetic directional valve, a 13-a first working oil port of the third electromagnetic directional valve, B13-a second working oil port of the third electromagnetic directional valve, a 14-an inlet of the first check valve, B14-an outlet of the first check valve, a 15-an inlet of the second check valve, B15-an outlet of the second check valve, a 20-an inlet of the second filter, B20-an outlet of the second check valve, a 21-an inlet of the fourth check valve, and 21-a fourth check valve, p22-the inlet of the second pressure reducing valve, A22-the outlet of the second pressure reducing valve, T22-the oil discharge port of the second pressure reducing valve, A23-the inlet of the fifth check valve, B23-the outlet of the fifth check valve, P24-the inlet of the third three-way proportional pressure reducing valve, A24-the outlet of the third three-way proportional pressure reducing valve, T24-the oil discharge port of the third three-way proportional pressure reducing valve, P25-the inlet of the fourth electromagnetic directional control valve, T25-the oil return port of the fourth electromagnetic directional control valve, A25-the first working oil port of the fourth electromagnetic directional control valve, B25-the second working oil port of the fourth electromagnetic directional control valve, P26-the inlet of the fourth three-way proportional pressure reducing valve, A26-the outlet of the fourth three-way proportional pressure reducing valve, T26-the oil discharge port of the fourth three-way proportional pressure reducing valve, A27-the inlet of the third check valve, B27-the outlet of the third check valve, X27-the check valve, and the third check valve 28-the inlet of the fourth, b28-an outlet of a fourth hydraulic control check valve, X28-a control oil port of the fourth hydraulic control check valve, A30-an inlet of the sixth check valve, B30-an outlet of the sixth check valve, P31-an inlet of a fifth electromagnetic directional valve, T31-an oil return port of the fifth electromagnetic directional valve, A31-a first working oil port of the fifth electromagnetic directional valve, B31-a second working oil port of the fifth electromagnetic directional valve, A32-an inlet of a third cut-off valve, B32-an outlet of the third cut-off valve, A33-an inlet of the fourth cut-off valve, B33-an outlet of the fourth cut-off valve, SF 1-an electrical code of a differential pressure transmitter of a first filter, SF 2-an electrical code of the differential pressure transmitter of a second filter, SV 1-an electrical control code of a pressure reducing valve of a first three-way ratio, SV 2-an electrical control code of the pressure reducing valve of the second three-way ratio, SF 3-an electrical code of the SV 4-a pressure reducing valve of the third three-way ratio, DT1, DT 2-the electromagnet control code of the first electromagnetic directional valve, DT3, DT 4-the electromagnet control code of the fourth electromagnetic directional valve, DT5, DT 6-the electromagnet control code of the second electromagnetic directional valve, DT7, DT 8-the electromagnet control code of the third electromagnetic directional valve, DT9, DT 10-the electromagnet control code of the fifth electromagnetic directional valve, Pr 1-the set pressure of the first pressure reducing valve, Pr 2-the set pressure of the second pressure reducing valve, P01-the nitrogen charging pressure of the first accumulator, P02-the nitrogen charging pressure of the second accumulator.
Detailed Description
The invention is described in further detail below with reference to the figures and the specific embodiments.
As shown in figure 1, the hydraulic tension system of the straight pull type cold/warm rolling experiment machine comprises a constant pressure oil source system 45, a left hydraulic clamp 41, a right hydraulic clamp 43, a left tension oil cylinder, a right tension oil cylinder, a left tension control unit I and a right tension control unit II, wherein the left hydraulic clamp 41 is connected with a piston rod of the left tension oil cylinder, a left tensiometer 40 is arranged at the joint of the left hydraulic clamp 41 and the left tension oil cylinder, the right hydraulic clamp 43 is connected with a piston rod of the right tension oil cylinder, a right tensiometer 42 is arranged at the joint of the right hydraulic clamp 43 and the right tension oil cylinder, a rolled piece is clamped between the left hydraulic clamp 41 and the right hydraulic clamp 43, the rolled piece is rolled back and forth by a rolling mill 44 while being tensioned by the left tension oil cylinder and the right tension oil cylinder, a high pressure oil outlet Ps of the constant pressure oil source system 45 is respectively communicated with a high pressure oil inlet K11 of the left tension control unit I and a high pressure inlet K21 of the right tension control unit, the back pressure oil outlet P0 of the constant pressure oil source system is communicated with a back pressure oil inlet K12 of the left tension control unit I, an oil return port T of the constant pressure oil source system is respectively communicated with an oil return port K14 of the left tension control unit I and an oil return port K23 of the right tension control unit II, and the back pressure oil outlet K13 of the left tension control unit I is communicated with a back pressure oil inlet K22 of the right tension control unit II.
The left tension control unit I comprises a first filter 1, a first check valve 2, a first pressure reducing valve 3, a second check valve 4, a first three-way proportional pressure reducing valve 5, a first electromagnetic directional valve 6, a second three-way proportional pressure reducing valve 7, a first hydraulic control check valve 8, a second hydraulic control check valve 9, a first energy accumulator 10, a third check valve 11, a second electromagnetic directional valve 12, a third electromagnetic directional valve 13, a first stop valve 14, a second stop valve 15, a first oil pressure sensor 16, a second oil pressure sensor 17 and a first pressure gauge 38; a high-pressure oil inlet K11 of the left tension control unit I is communicated with an inlet A1 of a first filter 1, an outlet B1 of the first filter 1 is communicated with an inlet A2 of a first check valve 2, an outlet B2 of the first check valve 2 is respectively communicated with an inlet P5 of a first three-way proportional pressure reducing valve 5, an inlet P6 of a first electromagnetic directional valve 6 and an inlet P3 of the first pressure reducing valve 3, an outlet A3 of the first pressure reducing valve 3 is respectively communicated with an inlet P7 of a second three-way proportional pressure reducing valve 7, a first accumulator 10 and a first pressure gauge 38, an oil outlet T5 of the first three-way proportional pressure reducing valve 5 is respectively communicated with an outlet B4 of the second check valve 4, an oil outlet T7 of the second three-way proportional pressure reducing valve 7, an oil outlet T3 of the first pressure reducing valve 3, an oil return port T13 of the third electromagnetic directional valve 13 and an inlet A11 of the third check valve 11, an inlet A4 of the second check valve 364 is communicated with an electromagnetic directional valve T6 of the first check valve 396, a control port X8 of the first pilot-operated check valve 8 is communicated with a first working port A6 of the first solenoid directional valve 6, a second working port B6 of the first solenoid directional valve 6 is communicated with a control port X9 of the second pilot-operated check valve 9, an inlet A9 of the second pilot-operated check valve 9 is communicated with an outlet A7 of the second three-way proportional pressure reducing valve 7, an inlet A8 of the first pilot-operated check valve 8 is respectively communicated with an outlet B9 of the second pilot-operated check valve 9 and an inlet P13 of the third solenoid directional valve 13, an oil return port T12 of the second solenoid directional valve 12 is communicated with an outlet B11 of the third check valve 11 and an oil return port K14 of the left tension control unit I, an inlet P12 of the second solenoid directional valve 12 is communicated with a backpressure oil inlet K12 of the left tension control unit I, a first working port A12 of the second solenoid directional valve 12 is respectively communicated with a backpressure oil outlet K13 of the left tension control unit I, a first oil pressure sensor and a14 of the first tension sensor 3614, an outlet B14 of the first stop valve 14 is communicated with a first working oil port K15 of the left tension control unit I, a first working oil port A13 of the third electromagnetic directional valve 13 is respectively communicated with an inlet A15 of the second stop valve 15 and the second oil pressure sensor 17, an outlet B15 of the second stop valve 15 is communicated with a second working oil port K16 of the left tension control unit I, a first working oil port K15 of the left tension control unit I is communicated with a rodless cavity of the left tension oil cylinder, and a second working oil port K16 of the left tension control unit I is communicated with a rod cavity of the left tension oil cylinder.
The right tension control unit II comprises a second filter 20, a fourth check valve 21, a second pressure reducing valve 22, a fifth check valve 23, a third three-way proportional pressure reducing valve 24, a fourth electromagnetic directional valve 25, a fourth three-way proportional pressure reducing valve 26, a third hydraulic control check valve 27, a fourth hydraulic control check valve 28, a second energy accumulator 29, a sixth check valve 30, a fifth electromagnetic directional valve 31, a third stop valve 32, a fourth stop valve 33, a third oil pressure sensor 34, a fourth oil pressure sensor 35 and a second pressure gauge 39; a high-pressure oil inlet K21 of the right tension control unit II is communicated with an inlet A20 of a second filter 20, an outlet B20 of the second filter 20 is communicated with an inlet A21 of a fourth check valve 21, an outlet B21 of the fourth check valve 21 is respectively communicated with an inlet P24 of a third three-way proportional pressure reducing valve 24, an inlet P25 of the fourth electromagnetic directional valve 25 and an inlet P22 of a second pressure reducing valve 22, an outlet A22 of the second pressure reducing valve 22 is respectively communicated with an inlet P26 of the fourth three-way proportional pressure reducing valve 26, a second accumulator 29 and a second pressure gauge 39, an oil discharge port T24 of the third three-way proportional pressure reducing valve 24 is communicated with an outlet B23 of a fifth check valve 23, an oil discharge port T26 of the fourth three-way proportional pressure reducing valve 26, an oil discharge port T22 of the second pressure reducing valve 22, an oil return port T31 of a fifth electromagnetic directional valve 31 and an inlet A30 of a sixth check valve 30, an inlet A23 of the fifth check valve 23 is communicated with an oil return port T25 of the fourth check valve, an outlet A24 of the third three-way proportional pressure reducing valve 24 is communicated with an outlet B27 of the third pilot-operated check valve 27, a control port X27 of the third pilot-operated check valve 27 is communicated with a first working port A25 of the fourth pilot-operated check valve 25, a second working port B25 of the fourth pilot-operated check valve 25 is communicated with a control port X28 of the fourth pilot-operated check valve 28, an inlet A28 of the fourth pilot-operated check valve 28 is communicated with an outlet A26 of the fourth three-way proportional pressure reducing valve 26, an inlet A27 of the third pilot-operated check valve 27 is communicated with an outlet B28 of the fourth pilot-operated check valve 28 and an inlet P31 of the fifth pilot-operated check valve 31, an outlet B30 of the sixth pilot-operated check valve 30 is communicated with an oil return port K23 of the right tension control unit II, a first working port A31 of the fifth pilot-operated check valve 31 is respectively communicated with an inlet A32 of the third check sensor 34 and the third check valve 32, and an outlet B32 of the right tension control unit 24 of the third check valve 32 are respectively communicated with a tension control, the back pressure oil inlet K22 of the right tension control unit II is communicated with the fourth oil pressure sensor 35 and the inlet A33 of the fourth stop valve 33, the outlet B33 of the fourth stop valve 33 is communicated with the second working oil port K25 of the right tension control unit II, the first working oil port K24 of the right tension control unit II is communicated with the rod cavity of the right tension oil cylinder, and the second working oil port K25 of the right tension control unit II is communicated with the rodless cavity of the right tension oil cylinder.
The left tension oil cylinder comprises a large-specification left tension oil cylinder 19.1 and a small-specification left tension oil cylinder 19.2, a first displacement sensor 18.1 is arranged in the large-specification left tension oil cylinder 19.1, a second displacement sensor 18.2 is arranged in the small-specification left tension oil cylinder 19.2, and the external connection size and the oil port size of the large-specification left tension oil cylinder 19.1 and the small-specification left tension oil cylinder 19.2 are the same.
The right tension oil cylinder comprises a large-specification right tension oil cylinder 37.1 and a small-specification right tension oil cylinder 37.2, a third displacement sensor 38.1 is arranged in the large-specification right tension oil cylinder 37.1, a fourth displacement sensor 38.2 is arranged in the small-specification right tension oil cylinder 37.2, and the external connection size and the oil port size of the large-specification right tension oil cylinder 19.1 and the small-specification right tension oil cylinder 19.2 are the same.
The large-specification left tension oil cylinder 19.1 and the large-specification right tension oil cylinder 37.1 are the same in model, and the small-specification left tension oil cylinder 19.2 and the small-specification right tension oil cylinder 37.2 are the same in model.
When steel materials are rolled under high tension (4-50kN), a first working oil port K15 of the left tension control unit I is communicated with a rodless cavity of the large-specification left tension oil cylinder 19.1, a second working oil port K16 of the left tension control unit I is communicated with a rod cavity of the large-specification left tension oil cylinder 19.1, a first working oil port K24 of the right tension control unit II is communicated with a rod cavity of the large-specification right tension oil cylinder 37.1, and a second working oil port K25 of the right tension control unit II is communicated with a rodless cavity of the large-specification right tension oil cylinder 37.1.
When the magnesium alloy material is rolled under small tension (0.5-4kN), a first working oil port K15 of the left tension control unit I is communicated with a rodless cavity of the small-specification left tension oil cylinder 19.2, a second working oil port K16 of the left tension control unit I is communicated with a rod cavity of the small-specification left tension oil cylinder 19.2, a first working oil port K24 of the right tension control unit II is communicated with a rod cavity of the small-specification right tension oil cylinder 37.2, and a second working oil port K25 of the right tension control unit II is communicated with a rodless cavity of the small-specification right tension oil cylinder 37.2.
The first energy accumulator 10 and the second energy accumulator 29 are both leather bag type energy accumulators; the first three-way proportional pressure reducing valve 5 and the third three-way proportional pressure reducing valve 24 have the same model, and the rated flow and pressure adjusting range is large, so that the requirement of large tension control is met; the second three-way proportional pressure reducing valve 7 and the fourth three-way proportional pressure reducing valve 26 have the same model, have smaller rated flow and pressure adjusting range, and are more favorable for realizing high-precision small tension control.
In this embodiment, the pressure setting value of the high-pressure oil outlet Ps of the constant-pressure oil source system is 23.5MPa, the pressure value of the back-pressure oil outlet P0 of the constant-pressure oil source system is 1.5MPa, the setting pressures of the first pressure reducing valve 3 and the second pressure reducing valve 22 are both 11MPa, and the nitrogen charging pressures of the first accumulator 10 and the second accumulator 29 are both 8 MPa; the models of the first filter 1 and the second filter 20 are ZU-H-250X3FP, the models of the first check valve 2, the second check valve 4, the third check valve 11, the fourth check valve 21, the fifth check valve 23 and the sixth check valve 30 are M-SR25KE00-10/B, the models of the first reducing valve 3 and the second reducing valve 22 are ZDR6DA1-50/100YM, the models of the first three-way proportional reducing valve 5 and the third three-way proportional reducing valve 24 are KZGO-AE-031/210 (rated flow 100L/min, pressure adjusting range 0-21MPa, control signal 0-10V), the models of the first electromagnetic reversing valve 6 and the fourth electromagnetic reversing valve 25 are 4WE6J60B/CG24N9Z 855Z 5L, the models of the second three-way proportional 7 and the fourth three-way proportional reducing valve 26 are RZAE-033/100 (rated flow 40L/min, the pressure adjusting range is 0-10MPa, the control signals are 0-10V), the models of the first hydraulic control check valve 8, the second hydraulic control check valve 9, the third hydraulic control check valve 27 and the fourth hydraulic control check valve 28 are SV20PA2-40B, the models of the first accumulator 10 and the second accumulator 29 are NXQ1-4L/31.5-F-A, the models of the second electromagnetic reversing valve 12, the third electromagnetic reversing valve 13 and the fifth electromagnetic reversing valve 31 are 4WE10E60B/CG24N9Z5L, the models of the first stop valve 14, the second stop valve 15, the third stop valve 32 and the fourth stop valve 33 are QJH-25B, the models of the first oil pressure sensor 16 and the fourth oil pressure sensor 35 are HDA3844-A-100-, the models of the first displacement sensor 18.1, the second displacement sensor 18.2, the third displacement sensor 36.1 and the fourth displacement sensor 36.2 are all RHM2150MD701SIG2100, the specifications of the first pressure gauge 38 and the second pressure gauge 39 are both 213.53.100/15MPa-G1/2, the specifications of the large-specification left tension oil cylinder 19.1 and the large-specification right tension oil cylinder 37.1 are shown in figures 2-4, the piston diameter is 90mm, the piston rod diameter is 63mm, the stroke is 2100mm, the specifications of the small-specification left tension oil cylinder 19.2 and the small-specification right tension oil cylinder 37.2 are shown in figures 5-7, and the piston diameter is 50mm, the piston rod diameter is 40mm, and the stroke is 2100 mm.
A control method of a hydraulic tension system of a straight-pull cold/warm rolling experiment machine adopts the hydraulic tension system of the straight-pull cold/warm rolling experiment machine, and comprises the following steps:
step 1: before the system operates for the first time, nitrogen is respectively filled into the first energy accumulator 10 and the second energy accumulator 29 through nitrogen cylinders, and the nitrogen filling pressure is 8 MPa;
step 2: after the constant-pressure oil source system is started for the first time, manually adjusting by observing the readings of the first pressure gauge 38 and the second pressure gauge 39, and adjusting the set pressure of the first pressure reducing valve 3 and the set pressure of the second pressure reducing valve 22 to 11 MPa;
and step 3: selecting the specifications of a left tension oil cylinder and a right tension oil cylinder according to the requirements of the rolling process;
when a steel material is rolled under high tension of 4-50kN, selecting a large-specification left tension oil cylinder 19.1 and a large-specification right tension oil cylinder 37.1 to perform tension loading on a rolled piece, marking the large-specification left tension oil cylinder 19.1 in a working state as C1, and marking the large-specification right tension oil cylinder 37.1 in the working state as C2; when the magnesium alloy material is rolled under the low tension of 0.5-4kN, a small-specification left tension oil cylinder 19.2 and a small-specification right tension oil cylinder 37.2 are selected to carry out tension loading on a rolled piece, the small-specification left tension oil cylinder 19.2 in a working state is marked as C1, and the small-specification right tension oil cylinder 37.2 in the working state is marked as C2; if the left tension oil cylinder and the right tension oil cylinder which are communicated with the left tension control unit I and the right tension control unit II at present are not consistent with the required tension oil cylinder, the constant pressure oil source system needs to be closed, after the pressures measured by the first oil pressure sensor 16, the second oil pressure sensor 17, the third oil pressure sensor 34 and the fourth oil pressure sensor 35 are all returned to zero, the first stop valve 14, the second stop valve 15, the third stop valve 32 and the fourth stop valve 33 are all closed, the tension oil cylinder is replaced, after the replacement, the first stop valve 14, the second stop valve 15, the third stop valve 32 and the fourth stop valve 33 are all opened, and then the constant pressure oil source system is started;
(II) determining the current working mode or state of each valve group according to the process selection result:
when rolling with large tension of 4-50kN is carried out, the control signals of the second three-way proportional pressure reducing valve 7 and the fourth three-way proportional pressure reducing valve 26 are 0 percent of the rated signal of the valve, namely 0V, the control signals of the first three-way proportional pressure reducing valve 5 and the third three-way proportional pressure reducing valve 24 are 20-30 percent of the rated signal of the valve, namely 2-3V, the first three-way proportional pressure reducing valve 5 for closed-loop tension control is marked as V1, the third three-way proportional pressure reducing valve 24 for closed-loop tension control is marked as V2, and the electromagnet DT2 of the first electromagnetic reversing valve 6 and the electromagnet DT4 of the fourth electromagnetic reversing valve 25 are controlled to be electrified; the outlet pressure of the second three-way proportional pressure reducing valve 7 and the fourth three-way proportional pressure reducing valve 26 is zero, namely the pressure at the inlet A9 of the second pilot-operated check valve 9 and the pressure at the inlet A28 of the fourth pilot-operated check valve 28 are zero, since the control port X9 of the second pilot check valve 9 and the control port X28 of the fourth pilot check valve 28 return at this time, at the same time, the control port X8 of the first pilot-controlled check valve 8 and the control port X27 of the third pilot-controlled check valve 27 are communicated with high-pressure oil and are in an open state, therefore, the outlet a5 of the first three-way proportional pressure reducing valve 5 is in a communication state with the inlet P13 of the third electromagnetic directional valve 13, the pressure is greater than zero, the outlet a24 of the third three-way proportional pressure reducing valve 24 is in a communication state with the inlet P31 of the fifth electromagnetic directional valve 31, the pressure is greater than zero, and the second hydraulic check valve 9 and the fourth hydraulic check valve 28 are in a two-way closing state under the action of pressure difference;
when the rolling with small tension of 0.5-4kN is carried out, the control signals of the first three-way proportional pressure reducing valve 5 and the third three-way proportional pressure reducing valve 24 are 80 percent of the rated signal of the valve, namely 8V, the control signals of the second three-way proportional pressure reducing valve 7 and the fourth three-way proportional pressure reducing valve 26 are 30-40 percent of the rated signal of the valve, namely 3-4V, the second three-way proportional pressure reducing valve 5 for tension closed-loop control is marked as V1, the fourth three-way proportional pressure reducing valve 26 for tension closed-loop control is marked as V2, and the electromagnet DT1 of the first electromagnetic reversing valve 6 and the electromagnet DT3 of the fourth electromagnetic reversing valve 25 are controlled to be electrified; the outlet pressures of the first three-way proportional pressure reducing valve 5 and the third three-way proportional pressure reducing valve 24 are higher than the rated pressures of the second three-way proportional pressure reducing valve 7 and the fourth three-way proportional pressure reducing valve 26, and because the control oil port X8 of the first pilot-controlled check valve 8 and the control oil port X27 of the third pilot-controlled check valve 27 return oil at this time, the first pilot-controlled check valve 8 and the third pilot-controlled check valve 27 are in a two-way closed state under the action of pressure difference, the outlet a7 of the second three-way proportional pressure reducing valve 7 and the inlet P13 of the third electromagnetic directional valve 13 are in a communicated state and the pressure is greater than zero, and the outlet a26 of the fourth three-way proportional pressure reducing valve 26 and the inlet P31 of the fifth electromagnetic directional valve 31 are in a communicated;
and 4, step 4: controlling an electromagnet DT6 of the second electromagnetic directional valve 12 to be electrified so as to lead the rodless cavities of the two tension oil cylinders to be communicated with the back pressure oil; the extension, retraction and stop actions of the large-specification left tension oil cylinder 19.1/the small-specification left tension oil cylinder 19.2 can be respectively realized by inching and controlling the power on/off of the two electromagnets DT7 and DT8 of the third electromagnetic directional valve 13; the extension, retraction and stop actions of the large-specification right tension oil cylinder 37.1/the small-specification right tension oil cylinder 37.2 can be respectively realized by inching and controlling the power on/off of the two electromagnets DT9 and DT10 of the fifth electromagnetic directional valve 31; thereby completing the clamping work of the rolled piece;
and 5: controlling the roll gap to the first secondary roll gap through a roll gap control system of the rolling mill; then, tension of the rolled piece is established, and the tension of the rolled piece is established in two ways:
(1) keeping the power-on state of an electromagnet DT6 of the second electromagnetic directional valve 12, keeping a marked variable By of 1, controlling the electromagnet DT8 of the third electromagnetic directional valve 13 and the electromagnet DT10 of the fifth electromagnetic directional valve 31 to be powered on, simultaneously putting a three-way proportional pressure reducing valve marked as V1 and a left tensiometer into left tension closed-loop control, putting the three-way proportional pressure reducing valve marked as V2 and the right tensiometer into right tension closed-loop control, and establishing outlet tension and inlet tension for the rolled piece according to a tension rule;
(2) controlling an electromagnet DT5 of the second electromagnetic reversing valve 12 to be electrified, wherein a marked variable By is 0, controlling an electromagnet DT8 of the third electromagnetic reversing valve 13 and an electromagnet DT10 of the fifth electromagnetic reversing valve 31 to be electrified, simultaneously putting a three-way proportional pressure reducing valve marked as V1 and a left tensiometer into left tension closed-loop control, putting the three-way proportional pressure reducing valve marked as V2 and the right tensiometer into right tension closed-loop control, and establishing outlet tension and inlet tension for a rolled piece according to a tension rule;
step 6: reversible cold/warm rolling is carried out on the rolled piece according to a rolling schedule compiled by a user according to specific conditions;
and 7: after the rolling is finished, the rolling mill is in a stop state, the tension of the outlet and inlet of a rolled piece is adjusted to zero through the tension closed-loop control in the step 5, the electromagnets DT8 of the third electromagnetic directional valve 13 and the electromagnets DT10 of the fifth electromagnetic directional valve 31 are controlled to be powered off, and the control signals of the two three-way proportional pressure reducing valves marked as V1 and V2 are restored to the values determined in the step 3; if the variable By set in the step 5 is 1, directly entering a step 8; if the variable By set in the step 5 is 0, controlling the electromagnet DT6 of the second electromagnetic directional valve 12 to be electrified;
and 8: and opening the left hydraulic clamp, controlling the two tension oil cylinders marked as C1 and C2 to retract, opening the right hydraulic clamp, taking down the rolled piece, setting the electromagnet states of all the electromagnetic directional valves to zero, setting all three-way proportional pressure reducing valve control signals to zero, and ending the experiment.
In the above description, when it is required to control a certain electromagnet of a certain electromagnetic directional valve to be powered on, another electromagnet of the same valve is controlled to be powered off by default.
The embodiments are not intended to limit the scope of the present invention, and all equivalent implementations or modifications without departing from the scope of the present invention are intended to be included in the scope of the present invention.

Claims (8)

1. A hydraulic tension system of a straight pull type cold/warm rolling experiment machine is characterized by comprising a constant pressure oil source system, a left hydraulic clamp, a right hydraulic clamp, a left tension oil cylinder, a right tension oil cylinder, a left tension control unit and a right tension control unit, wherein the left hydraulic clamp is connected with a piston rod of the left tension oil cylinder, a left tensiometer is arranged at the joint of the left hydraulic clamp and the left tension oil cylinder, the right hydraulic clamp is connected with a piston rod of the right tension oil cylinder, a right tensiometer is arranged at the joint of the right hydraulic clamp and the right tension oil cylinder, a rolling piece is clamped between the left hydraulic clamp and the right hydraulic clamp, the rolling piece is rolled in a reciprocating manner by a rolling mill while tension is exerted by the left tension oil cylinder and the right tension oil cylinder, a high pressure oil outlet of the constant pressure oil source system is respectively communicated with a high pressure oil inlet of the left tension control unit and a high pressure inlet of the right tension control, a back pressure oil outlet of the constant pressure oil source system is communicated with a back pressure oil inlet of the left tension control unit, an oil return port of the constant pressure oil source system is respectively communicated with an oil return port of the left tension control unit and an oil return port of the right tension control unit, and a back pressure oil outlet of the left tension control unit is communicated with a back pressure oil inlet of the right tension control unit;
the left tension control unit comprises a first filter, a first one-way valve, a first pressure reducing valve, a second one-way valve, a first three-way proportional pressure reducing valve, a first electromagnetic directional valve, a second three-way proportional pressure reducing valve, a first hydraulic control one-way valve, a second hydraulic control one-way valve, a first energy accumulator, a third one-way valve, a second electromagnetic directional valve, a third electromagnetic directional valve, a first stop valve, a second stop valve, a first oil pressure sensor, a second oil pressure sensor and a first pressure gauge; the high-pressure oil inlet of the left tension control unit is communicated with the inlet of a first filter, the outlet of the first filter is communicated with the inlet of a first one-way valve, the outlet of the first one-way valve is respectively communicated with the inlet of a first three-way proportional pressure reducing valve, the inlet of a first electromagnetic directional valve and the inlet of the first pressure reducing valve, the outlet of the first pressure reducing valve is respectively communicated with the inlet of a second three-way proportional pressure reducing valve, a first energy accumulator and a first pressure gauge, the oil discharge port of the first three-way proportional pressure reducing valve is respectively communicated with the outlet of the second one-way valve, the oil discharge port of the second three-way proportional pressure reducing valve, the oil discharge port of the first pressure reducing valve, the oil return port of a third electromagnetic directional valve and the inlet of the third one-way valve, the inlet of the second one-way valve is communicated with the oil return port of the first electromagnetic directional valve, the control oil return port, a second working oil port of the first electromagnetic directional valve is communicated with a control oil port of a second hydraulic control one-way valve, an inlet of the second hydraulic control one-way valve is communicated with an outlet of a second three-way proportional pressure reducing valve, an inlet of the first hydraulic control one-way valve is respectively communicated with an outlet of the second hydraulic control one-way valve and an inlet of a third electromagnetic directional valve, an oil return port of the second electromagnetic directional valve is communicated with an outlet of the third one-way valve and an oil return port of the left tension control unit, an inlet of the second electromagnetic directional valve is communicated with a back pressure oil inlet of the left tension control unit, a first working oil port of the second electromagnetic directional valve is respectively communicated with a back pressure oil outlet of the left tension control unit, a first oil pressure sensor and an inlet of a first stop valve, an outlet of the first stop valve is communicated with a first working oil port of the left tension control unit, and a first working oil port of the third electromagnetic directional valve is respectively communicated with an inlet of the second, an outlet of the second stop valve is communicated with a second working oil port of the left tension control unit, a first working oil port of the left tension control unit is communicated with a rodless cavity of the left tension oil cylinder, and a second working oil port of the left tension control unit is communicated with a rod cavity of the left tension oil cylinder;
the right tension control unit comprises a second filter, a fourth one-way valve, a second pressure reducing valve, a fifth one-way valve, a third three-way proportional pressure reducing valve, a fourth electromagnetic directional valve, a fourth three-way proportional pressure reducing valve, a third hydraulic control one-way valve, a fourth hydraulic control one-way valve, a second energy accumulator, a sixth one-way valve, a fifth electromagnetic directional valve, a third stop valve, a fourth stop valve, a third oil pressure sensor, a fourth oil pressure sensor and a second pressure gauge; the high-pressure oil inlet of the right tension control unit is communicated with the inlet of a second filter, the outlet of the second filter is communicated with the inlet of a fourth one-way valve, the outlet of the fourth one-way valve is respectively communicated with the inlet of a third three-way proportional pressure reducing valve, the inlet of a fourth electromagnetic directional valve and the inlet of a second pressure reducing valve, the outlet of the second pressure reducing valve is respectively communicated with the inlet of the fourth three-way proportional pressure reducing valve, a second energy accumulator and a second pressure gauge, the oil discharge port of the third three-way proportional pressure reducing valve is communicated with the outlet of a fifth one-way valve, the oil discharge port of the fourth three-way proportional pressure reducing valve, the oil discharge port of the second pressure reducing valve, the oil return port of the fifth electromagnetic directional valve and the inlet of a sixth one-way valve, the inlet of the fifth one-way valve is communicated with the oil return port of the fourth electromagnetic directional valve, the outlet of the third three-way proportional pressure reducing valve is communicated with the outlet of the third hydraulic control, a second working oil port of the fourth electromagnetic directional valve is communicated with a control oil port of the fourth hydraulic control one-way valve, an inlet of the fourth hydraulic control one-way valve is communicated with an outlet of a fourth three-way proportional pressure reducing valve, an inlet of the third hydraulic control one-way valve is communicated with an outlet of the fourth hydraulic control one-way valve and an inlet of a fifth electromagnetic directional valve, an outlet of the sixth one-way valve is communicated with an oil return port of the right tension control unit, a first working oil port of the fifth electromagnetic directional valve is respectively communicated with an inlet of a third oil pressure sensor and an inlet of a third stop valve, an outlet of the third stop valve is communicated with a first working oil port of the right tension control unit, a back pressure oil inlet of the right tension control unit is communicated with the fourth oil pressure sensor and an inlet of the fourth stop valve, an outlet of the fourth stop valve is communicated with a second working oil port of the right tension control unit, a first working oil port of the right tension control unit is communicated, and a second working oil port of the right tension control unit is communicated with a rodless cavity of the right tension oil cylinder.
2. The hydraulic tension system of the straight pull cold/warm rolling test machine as claimed in claim 1, wherein: the left tension oil cylinder comprises a large-specification left tension oil cylinder and a small-specification left tension oil cylinder, a first displacement sensor is arranged in the large-specification left tension oil cylinder, a second displacement sensor is arranged in the small-specification left tension oil cylinder, and the external connection size and the oil port size of the large-specification left tension oil cylinder are the same as those of the small-specification left tension oil cylinder.
3. The hydraulic tension system of the straight pull cold/warm rolling test machine as claimed in claim 2, wherein: the right tension oil cylinder comprises a large-specification right tension oil cylinder and a small-specification right tension oil cylinder, a third displacement sensor is arranged in the large-specification right tension oil cylinder, a fourth displacement sensor is arranged in the small-specification right tension oil cylinder, and the external connection size and the oil port size of the large-specification right tension oil cylinder are the same as those of the small-specification right tension oil cylinder.
4. The hydraulic tension system of the straight pull cold/warm rolling test machine according to claim 3, wherein: the large-specification left tension oil cylinder and the large-specification right tension oil cylinder are the same in model, and the small-specification left tension oil cylinder and the small-specification right tension oil cylinder are the same in model.
5. The hydraulic tension system of the straight pull cold/warm rolling test machine as claimed in claim 4, wherein: when the steel material is rolled under high tension of 4-50kN, a first working oil port of the left tension control unit is communicated with a rodless cavity of the large-specification left tension oil cylinder, a second working oil port of the left tension control unit is communicated with a rod cavity of the large-specification left tension oil cylinder, a first working oil port of the right tension control unit is communicated with a rod cavity of the large-specification right tension oil cylinder, and a second working oil port of the right tension control unit is communicated with a rodless cavity of the large-specification right tension oil cylinder.
6. The hydraulic tension system of the straight pull cold/warm rolling test machine as claimed in claim 4, wherein: when the magnesium alloy material is rolled under the small tension of 0.5-4kN, a first working oil port of the left tension control unit is communicated with a rodless cavity of the small-specification left tension oil cylinder, a second working oil port of the left tension control unit is communicated with a rod cavity of the small-specification left tension oil cylinder, a first working oil port of the right tension control unit is communicated with a rod cavity of the small-specification right tension oil cylinder, and a second working oil port of the right tension control unit is communicated with the rodless cavity of the small-specification right tension oil cylinder.
7. The hydraulic tension system of the straight pull cold/warm rolling test machine as claimed in claim 1, wherein: the first energy accumulator and the second energy accumulator both adopt leather bag type energy accumulators, and the first three-way proportional pressure reducing valve and the third three-way proportional pressure reducing valve have the same model; the second three-way proportional pressure reducing valve and the fourth three-way proportional pressure reducing valve have the same model.
8. A control method of hydraulic tension of a straight pull type cold/warm rolling experiment machine, which adopts the hydraulic tension system of the straight pull type cold/warm rolling experiment machine as claimed in claim 1, is characterized by comprising the following steps:
step 1: before the system operates for the first time, a nitrogen cylinder is used for filling nitrogen into the first energy accumulator, and the nitrogen filling pressure is 0.75 time of the set pressure of the first pressure reducing valve; filling nitrogen into the second energy accumulator through a nitrogen cylinder, wherein the nitrogen filling pressure is 0.75 times of the set pressure of the second pressure reducing valve;
step 2: starting the constant-pressure oil source system, and adjusting the set pressure of the first pressure reducing valve to be 1-3MPa higher than the rated adjusting pressure of the second three-way proportional pressure reducing valve; the set pressure of the second pressure reducing valve is regulated to be 1-3MPa higher than the rated regulation pressure of the fourth three-way proportional pressure reducing valve;
and step 3: selecting the specification of a tension oil cylinder according to the requirements of a rolling process, namely selecting a large-specification left tension oil cylinder and a large-specification right tension oil cylinder to perform tension loading on a rolled piece when a steel material is rolled at a high tension of 4-50 kN; when the magnesium alloy material is rolled with small tension of 0.5-4kN, a small-specification left tension oil cylinder and a small-specification right tension oil cylinder are selected to carry out tension loading on a rolled piece; marking the left tension oil cylinder in a working state as C1, and marking the right tension oil cylinder in a working state as C2; if the tension oil cylinders communicated with the left tension control unit and the right tension control unit are not consistent with the required oil cylinders at present, the constant-pressure oil source system needs to be closed, after the pressures measured by the first oil pressure sensor, the second oil pressure sensor, the third oil pressure sensor and the fourth oil pressure sensor are all returned to zero, the first stop valve, the second stop valve, the third stop valve and the fourth stop valve are all closed, the tension oil cylinders are replaced, the first stop valve, the second stop valve, the third stop valve and the fourth stop valve are all opened after the replacement is finished, and then the constant-pressure oil source system is started; then, according to the process selection result, determining the current working mode or state of each valve group: when rolling with large tension of 4-50kN is carried out, the control signals of the second three-way proportional pressure reducing valve and the fourth three-way proportional pressure reducing valve are 0% of the rated signal of the valve, the control signals of the first three-way proportional pressure reducing valve and the third three-way proportional pressure reducing valve are 20% -30% of the rated signal of the valve, and the electromagnet DT2 of the first electromagnetic reversing valve and the electromagnet DT4 of the fourth electromagnetic reversing valve are controlled to be powered; when the rolling is carried out under the low tension of 0.5-4kN, the control signals of the first three-way proportional pressure reducing valve and the third three-way proportional pressure reducing valve are 80% of the rated signal of the valve, and the control signals of the second three-way proportional pressure reducing valve and the fourth three-way proportional pressure reducing valve are 30% -40% of the rated signal of the valve; marking a first three-way proportional pressure reducing valve and a third three-way proportional pressure reducing valve for closed-loop tension control as V1 and V2, or marking a second three-way proportional pressure reducing valve and a fourth three-way proportional pressure reducing valve for closed-loop tension control as V1 and V2, and controlling an electromagnet DT1 of the first electromagnetic directional valve and an electromagnet DT3 of the fourth electromagnetic directional valve to be electrified;
and 4, step 4: controlling an electromagnet DT6 of the second electromagnetic directional valve to be electrified so as to lead the rodless cavities of the two tension oil cylinders to be communicated with the back pressure oil; the extending, retracting and stopping actions of the large-specification left tension oil cylinder or the small-specification left tension oil cylinder can be respectively realized by inching and controlling the power on or power off of the two electromagnets DT7 and DT8 of the third electromagnetic reversing valve; the stretching, retracting and stopping actions of the large-specification right tension oil cylinder or the small-specification right tension oil cylinder can be respectively realized by inching and controlling the power on or power off of two electromagnets DT9 and DT10 of the fifth electromagnetic reversing valve; thereby completing the clamping work of the rolled piece;
and 5: controlling the roll gap to the first secondary roll gap through a roll gap control system of the rolling mill; then, tension of the rolled piece is established, and the tension of the rolled piece is established in two ways:
(1) keeping the power-on state of an electromagnet DT6 of the second electromagnetic reversing valve, controlling the electromagnet DT8 of the third electromagnetic reversing valve and the electromagnet DT10 of the fifth electromagnetic reversing valve to be powered on with a marked variable By of 1, putting a three-way proportional pressure reducing valve marked as V1 and a left tensiometer into left tension closed-loop control, putting the three-way proportional pressure reducing valve marked as V2 and the right tensiometer into right tension closed-loop control, and establishing outlet tension and inlet tension for the rolled piece according to a tension rule;
(2) controlling an electromagnet DT5 of the second electromagnetic reversing valve to be electrified, controlling an electromagnet DT8 of the third electromagnetic reversing valve and an electromagnet DT10 of the fifth electromagnetic reversing valve to be electrified, simultaneously putting a V1 three-way proportional pressure reducing valve and a left tensiometer which are marked as V1 into left tension closed-loop control, putting the V2 three-way proportional pressure reducing valve and the right tensiometer into right tension closed-loop control, and establishing outlet tension and inlet tension for the rolled piece according to a tension rule;
step 6: reversible cold or warm rolling is carried out on the rolled piece according to the rolling schedule;
and 7: after the rolling is finished, the rolling mill is in a stop state, the tension of the outlet and inlet of a rolled piece is adjusted to be zero through the tension closed-loop control in the step five, the electromagnets DT8 of the third electromagnetic directional valve and the electromagnets DT10 of the fifth electromagnetic directional valve are controlled to be powered off, and the control signals of the two three-way proportional pressure reducing valves marked as V1 and V2 are restored to the numerical values determined in the step three; if the variable By set in the step 5 is 1, directly entering a step 8; if the variable By set in the step 5 is 0, controlling the electromagnet DT6 of the second electromagnetic directional valve to be electrified;
and 8: and opening the left hydraulic clamp, controlling the two tension oil cylinders marked as C1 and C2 to retract, opening the right hydraulic clamp, taking down the rolled piece, setting the electromagnet states of all the electromagnetic directional valves to zero, setting all three-way proportional pressure reducing valve control signals to zero, and ending the experiment.
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JP2021574747A JP7224696B2 (en) 2019-07-09 2019-07-17 HYDRAULIC TENSION SYSTEM AND CONTROL METHOD FOR THE DIRECT COLD/WARM ROLLING TESTER
PCT/CN2019/096263 WO2021003761A1 (en) 2019-07-09 2019-07-17 Hydraulic tension system of direct-pulling cold/warm rolling tester, and control method therefor

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