CN115059729B - Graded vibration damper based on electromagnetic and hydraulic damping - Google Patents
Graded vibration damper based on electromagnetic and hydraulic damping Download PDFInfo
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- CN115059729B CN115059729B CN202210825885.3A CN202210825885A CN115059729B CN 115059729 B CN115059729 B CN 115059729B CN 202210825885 A CN202210825885 A CN 202210825885A CN 115059729 B CN115059729 B CN 115059729B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
- F16F15/027—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means comprising control arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/03—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using magnetic or electromagnetic means
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Abstract
The utility model belongs to the technical field of rolling mill vibration reduction devices, and particularly relates to a grading vibration reduction device based on electromagnetic and hydraulic damping. Comprises a roller system damping device and a roller frame damping device; the roller system vibration damping device is used for suppressing vibration among roller systems; the roller system vibration damper comprises four vertical hydraulic cylinders which are hinged between a supporting seat of an upper working roller and a supporting seat of a lower working roller; the roller frame vibration damping device is used for suppressing vibration between the working roller and the frame; the roll stand vibration damping device comprises four transverse hydraulic cylinders, a connecting rod and a vibration damping stand; the connecting rod is used for connecting the supporting seat and the transverse hydraulic cylinder; the vibration reduction frame is positioned on the frame. The utility model has the characteristics of reasonable and simple structure, obvious vibration reduction effect, capability of utilizing magnetic force and hydraulic damping to suppress vibration of a rolling mill roller system and a frame in a grading manner, and capability of monitoring vibration conditions in real time.
Description
Technical Field
The utility model belongs to the technical field of rolling mill vibration reduction devices, and particularly relates to a grading vibration reduction device based on electromagnetic and hydraulic damping.
Background
With the rapid development and progress of science and technology and industry, the plate and strip materials are widely applied to various fields of automobiles, ships, aerospace and the like. In recent years, the demand for sheet materials in the modern industry is continuously increasing, and the requirements for sheet quality and dimensional accuracy are also continuously increasing. The production and processing of the plate strip are mainly finished by virtue of rolling mill equipment, and the phenomenon of vertical vibration frequently occurs in the rolling process, so that marks are left on the surfaces of rollers and the surfaces of plates, and the surface quality and the dimensional accuracy of the plate strip are adversely affected. Therefore, the vibration problem of the rolling mill has become a problem to be solved in the rolling production process of steel enterprises.
Therefore, it is important to design a grading vibration damper based on electromagnetic and hydraulic damping with a reasonable and simple structure and an obvious vibration damping effect.
For example, the damping vibration attenuation device of the hydraulic cylinder described in the Chinese patent application No. CN200820055585.7 comprises a cylinder body, a cylinder cover, a piston and a piston rod, wherein the right end of the cylinder body is fixedly connected with the cylinder cover to form a cavity, an opening is formed in the cylinder cover, the piston is arranged in the cavity, and the cavity is divided into a left part and a right part; the left end of the piston is provided with a lug, and the inner wall of the left end of the cylinder body is provided with a groove matched with the lug at the left end of the piston; the piston comprises a piston body and a piston cover, the right end of the piston body is fixedly connected with the piston cover to form a cavity, an opening is formed in the piston cover, the left end of the piston rod is in a step shape and is reversely buckled in the cavity, and an elastic damping body is filled between the left end of the piston rod and the inner wall of the piston body; the right end of the piston rod sequentially passes through the opening of the piston cover and the opening of the cylinder cover to be connected with the outside. The left end of the piston rod is provided with a lug, and the inner wall of the left end of the piston body is provided with a groove matched with the lug at the left end of the piston rod. Although the piston part in the hydraulic cylinder is improved on the basis of not influencing the original equipment structure, the piston and the piston rod which are originally connected into a whole are divided into two parts, an elastic damping body is arranged in a gap between the sealed cavity of the piston and the head part of the piston rod, and vibration energy generated in the rolling process is absorbed through the characteristics of the elastic damping body, so that the vibration of the cold rolling mill is reduced, the stability of the cold rolling mill is improved, the whole device is simple in structure, convenient to install and safe and reliable, but the device has the defects that the device only mainly improves the piston part in the hydraulic cylinder, thereby achieving the vibration reduction effect, cannot inhibit the vibration of a rolling mill roller system and a stand in a grading manner according to the actual vibration condition, cannot monitor the vibration condition in real time, and has poor integral vibration reduction effect.
Disclosure of Invention
The utility model provides the electromagnetic and hydraulic damping-based grading vibration damper which is reasonable and simple in structure and obvious in vibration damping effect, can be used for restraining vibration of a rolling mill roller system and a stand in a grading manner by utilizing magnetic force and hydraulic damping, and can be used for monitoring vibration in real time, so as to solve the problem that in the prior art, vertical vibration frequently occurs in a rolling process to cause impression on the surface of a roller and the surface of a plate and cause adverse effects on the surface quality and dimensional accuracy of a plate and a strip.
In order to achieve the aim of the utility model, the utility model adopts the following technical scheme:
the grading vibration damper based on electromagnetic and hydraulic damping comprises a frame, a lower working roller arranged on the frame, and an upper working roller arranged above the lower working roller; the outer parts of the lower working roller and the upper working roller are respectively provided with a supporting seat; the vibration damping device of the roller system and the vibration damping device of the roller frame are also included;
the roller system vibration damping device is used for suppressing vibration among roller systems; the roller system vibration damper comprises four vertical hydraulic cylinders which are hinged between a supporting seat of an upper working roller and a supporting seat of a lower working roller;
the roller frame vibration damping device is used for suppressing vibration between the working roller and the frame; the roll stand vibration damping device comprises four transverse hydraulic cylinders, a connecting rod and a vibration damping stand; the connecting rod is used for connecting the supporting seat and the transverse hydraulic cylinder and converting the vertical vibration of the working roller into the axial movement of the piston of the hydraulic cylinder; the transverse hydraulic cylinder is fixed on the vibration reduction frame, and the vibration reduction frame is positioned on the frame.
Preferably, the 2 proportional throttle valves comprise a first push rod, a sealing ring, a spring and a first ball; the first ball is positioned at the tail part of the push rod, and freely slides in the ball groove so as to enable the first push rod to move; the first push rod head is conical and used for controlling the opening of the valve port so as to regulate the oil flow at the valve port.
Preferably, the 2 proportion electromagnets comprise 2 conical push rods, balls, ball slides, movable iron cores, springs, T-shaped static iron cores, piezoresistive sensors and electromagnetic coils; the T-shaped static iron core is wound with an electromagnetic coil and is connected with the movable iron core through a spring; the movable iron core is in interference fit with the tapered push rods, the top ends of the 2 tapered push rods are designed into slideways with opposite taper and are provided with ball grooves, and balls are arranged at two sides of the cross-shaped design of the tail part of the tapered push rod and used for enabling the tapered push rods to freely slide in the ball slideways;
the magnetostrictive displacement sensor and the proportional electromagnet form electromagnetic compensation primary vibration reduction; the piezoresistive sensor and the proportional throttle valve return oil and discharge oil to the inner cavity and the outer cavity to form proportional throttle type secondary vibration reduction; the one-way throttle valve in the outer cavity returns oil to the rod cavity of the hydraulic cylinder to form the hydraulic damping three-stage vibration reduction.
Preferably, the piezoresistive sensor is fixed on a T-shaped static iron core; the magnetic sliding block drives the oil in the inner cavity to flow to form a pulse signal which acts on the piezoresistive sensor, the piezoresistive sensor transmits the pressure signal to the signal processing center, the pressure signal is converted into a current signal after being processed to obtain an error value, and the current of the proportional electromagnet coil is adjusted according to the error value to control the opening of the valve port of the proportional throttle valve, so that error value compensation is realized.
Preferably, the 2 proportional throttle valves comprise a first push rod, a sealing ring, a spring and a first ball; the first ball is positioned at the tail part of the push rod, and freely slides in the ball groove so as to enable the first push rod to move; the first push rod head is conical and used for controlling the opening of the valve port so as to regulate the oil flow at the valve port.
Preferably, the conical slide way at the top end of the conical push rod in the 2 proportion electromagnets acts on the push rod of the proportion throttle valve, and the directions of the two symmetrically arranged conical slide ways are opposite, so that the 2 proportion throttle valves are in one-way conduction and opposite in direction to respectively carry out proportion throttle on oil outlet compensation and oil return compensation of the inner cavity and the outer cavity.
Preferably, the transverse hydraulic cylinder comprises a piston push rod, a screw, a sealing ring, a second end cover, a permanent magnet piston, a core with a cavity, an electromagnetic coil, a semiconductor radiating fin, an outer cylinder body, a third one-way throttle valve, a fourth one-way throttle valve and a proportional throttle slide valve;
the iron core with the cavity is fixed in the middle of the transverse hydraulic cylinder; the electromagnetic coil is wound on the iron core with the cavity, and 6 semiconductor cooling fins which are uniformly distributed are arranged outside the electromagnetic coil; the third one-way throttle valve and the fourth one-way throttle valve are symmetrically embedded in the iron core with the cavity; the permanent magnet piston is internally embedded with a proportional electromagnet and a proportional throttle slide valve and is fixed on the piston push rod through a nut; the second end cover is fixedly connected to the outer cylinder body through a screw and is in clearance fit with the piston push rod; and the inner ring and the outer ring of the second end cover are respectively provided with a sealing ring for sealing the piston push rod and the outer cylinder body.
Preferably, the proportional throttle slide valve comprises a spring, a second push rod, a valve clack and a T-shaped fixed block; the tail part of the second push rod is provided with a second ball which freely slides in the ball groove so as to enable the second push rod to move; the second push rod drives the valve clack to slide, so that the opening control of the valve port is realized, and the oil flow at the valve port is further controlled; the spring is fixed on the T-shaped fixed block and is used for resetting the valve clack.
Preferably, the vibration reduction frame is made of high damping materials.
Compared with the prior art, the utility model has the beneficial effects that: (1) The vibration damping device comprises two vibration damping devices, four hydraulic cylinders which are vertically distributed can generate a damping effect on vibration among roller systems, and the hydraulic cylinders and the vibration damping frames which are transversely and symmetrically distributed can restrain vibration among working rollers and a frame; (2) The vertical hydraulic cylinder is designed to be of a double-cavity structure, and the piston is designed to be a coaxial double-piston. The inner cavity realizes preliminary magnetic damping through the reaction force generated by the interaction of the permanent magnet piston and the H-shaped iron core on the electromagnetic coil, and the outer cavity controls the opening of the valve port through the proportional electromagnet and the proportional throttle valve embedded in the cylinder body, so that hydraulic damping vibration damping is realized. The piston in the outer cavity is designed to be annular, and the damping effect can be further achieved by the embedded one-way throttle valve. In addition, the magnetic sliding block in the inner cavity can realize the storage and release of the oil in the outer cavity under the action of the magnetic field of the electromagnetic coil. The vibration damper can perform graded vibration damping according to actual vibration conditions, and has obvious vibration damping effect; (3) The transverse vibration damper comprises a connecting rod, a transverse hydraulic cylinder and a vibration damper frame. The connecting rod can convert the vertical vibration of the working roller into the axial movement of the piston of the hydraulic cylinder, and the hydraulic damping generated by the control of the opening degree of the valve port by the proportional electromagnet and the proportional throttle slide valve is further achieved by the magnetic force generated by the interaction of the iron core with the cavity on the coil and the piston, so that the grading vibration reduction effect between the working roller and the frame is further achieved. The vibration reduction rack of the high damping material can assist in vibration reduction of the rack; (4) The vibration damper comprises two sensors, one is a magnetostrictive displacement sensor, and mainly utilizes a strain pulse signal generated by the change of an intersecting magnetic field between the permanent magnet piston and the electromagnetic coil to accurately measure the displacement of the permanent magnet piston and further determine the vibration degree. The other is a piezoresistive sensor, a pulse signal is generated on the piezoresistive sensor when the magnetic sliding block drives oil to move, and the pulse signal is converted into a current signal through signal center processing to control the displacement of the movable iron core of the proportional magnet, so that the valve opening of the proportional throttle valve is adjusted, and the purpose of vibration reduction is achieved.
Drawings
FIG. 1 is a schematic diagram of a hierarchical vibration damper based on electromagnetic and hydraulic damping according to the present utility model;
FIG. 2 is a cross-sectional view of an overall construction of the vertical hydraulic cylinder of the present utility model;
FIG. 3 is an enlarged view of a portion of a vertical hydraulic cylinder of the present utility model;
FIG. 4 is a cross-sectional view of an overall construction of the transverse hydraulic cylinder of the present utility model;
fig. 5 is an enlarged view of a portion of a transverse cylinder according to the present utility model.
In the figure: the upper working roll 1, the transverse hydraulic cylinder 2, the connecting rod 3, the vibration reduction frame 4, the vertical hydraulic cylinder 5, the lower working roll 6, the supporting seat 7, the frame 8, the end cover 501, the screw 502, the sealing ring 503, the O-shaped sealing ring 504, the rubber gasket 505, the tensioning ring 506, the piston rod 507, the first one-way valve throttle 508, the second one-way throttle 509, the annular piston body 510, the permanent magnet piston 511, the nut 512, the H-shaped iron core 513, the electromagnetic coil 514, the spring 515, the sealing ring 516, the magnetic sliding block 517, the magnetostriction displacement sensor 518, the cylinder 519, the proportional electromagnet A, the proportional throttle B, the conical push rod A-1, the ball A-2, the piston rod 507, the first one-way valve throttle 508, the second one-way throttle 509, the annular piston body 510, the permanent magnet piston 511, the nut 512, the H-shaped iron core 513, the electromagnetic coil 514, the spring 515, the sealing ring 516, the magnetic sliding block 517, the magnetostriction displacement sensor 518, the cylinder 519, the proportional electromagnet A, the proportional throttle B, the conical push rod-2, the rubber gasket-ring-and the rubber ball slide A-3, moving iron core A-4, spring A-5, T-shaped static iron core A-6, piezoresistive sensor A-7, sealing ring A-8, sealing cover A-9, electromagnetic coil A-10, push rod B-1, sealing ring B-2, spring B-3, ball B-4, piston push rod 201, screw 202, sealing ring 203, sealing ring 204, end cover 205, permanent magnet piston 206, chambered iron core 207, electromagnetic coil 208, semiconductor cooling fin 209, outer cylinder 210, third one-way throttle valve 211, fourth one-way throttle valve 212, proportional throttle valve C, spring C-1, sealing ring C-2, push rod C-3, valve clack C-4, spring C-5, T-shaped fixed block C-6.
Detailed Description
In order to more clearly illustrate the embodiments of the present utility model, specific embodiments of the present utility model will be described below with reference to the accompanying drawings. It is evident that the drawings in the following description are only examples of the utility model, from which other drawings and other embodiments can be obtained by a person skilled in the art without inventive effort.
Example 1:
the grading vibration damper based on electromagnetic and hydraulic damping as shown in fig. 1 comprises a frame 8, a lower working roller 6 arranged on the frame, and an upper working roller 1 arranged above the lower working roller; the outer parts of the lower working roller and the upper working roller are respectively provided with a supporting seat 7; the vibration damping device of the roller system and the vibration damping device of the roller frame are also included;
the roller system vibration damping device is used for suppressing vibration among roller systems; the roller system vibration damper comprises four vertical hydraulic cylinders 5 which are hinged between a supporting seat of an upper working roller and a supporting seat of a lower working roller;
the roller frame vibration damping device is used for suppressing vibration between the working roller and the frame; the roll stand vibration damping device comprises four transverse hydraulic cylinders 2, a connecting rod 3 and a vibration damping stand 4; the connecting rod is used for connecting the supporting seat and the transverse hydraulic cylinder; the vibration reduction frame is positioned on the frame.
As shown in fig. 2 and 3, a vertical hydraulic cylinder is shown in a sectional view and a partially enlarged view. The utility model takes the vertical hydraulic cylinder as a vertical vibration damper. The vertical hydraulic cylinder comprises an end cover 501, a screw 502, a sealing ring 503, an O-shaped sealing ring 504, a rubber gasket 505, a tensioning ring 506, a piston rod 507, a first one-way valve throttle 508, a second one-way throttle 509, an annular piston body 510, a permanent magnet piston 511, a nut 512, an I-shaped iron core 513, an electromagnetic coil 514, a spring 515, a sealing ring 516, a magnetic sliding block 517, a magnetostrictive displacement sensor 518, a cylinder 519, a proportional electromagnet A and a proportional throttle B.
The upper end surface of the permanent magnet piston is provided with a magnetostrictive displacement sensor which is fixedly connected to the piston rod through a nut; the electromagnetic coil is wound on the I-shaped iron core, the I-shaped iron core is fixed in the middle of the inner cavity of the vertical hydraulic cylinder, and the upper end of the I-shaped iron core is connected with the magnetic sliding block through a spring; the magnetic sliding block is circumferentially provided with a sealing ring for sealing the external cavity oil; the proportional electromagnet and the proportional throttle valve are embedded in the outer cavity; the first one-way throttle valve and the second one-way throttle valve are embedded in the annular piston body; the piston rod is in threaded connection with the annular piston body, and the bottom of the piston rod is also provided with a tensioning ring and a rubber gasket; the end cover is fixedly connected to the cylinder body through a screw and is in clearance fit with the annular piston body; and the inner ring and the outer ring of the end cover are respectively provided with a sealing ring and an O-shaped sealing ring, and are used for sealing the annular piston body and the cylinder body.
The proportional electromagnet comprises a conical push rod A-1, a ball A-2, a ball slide way A-3, a movable iron core A-4, a spring A-5, a T-shaped static iron core A-6, a piezoresistive sensor A-7, a sealing ring A-8, a sealing cover A-9 and an electromagnetic coil A-10. The T-shaped static iron core is wound with an electromagnetic coil and is connected with the movable iron core through a spring; the movable iron core is in interference fit with the conical push rod, the head of the conical push rod is provided with a ball groove, and balls are arranged on two sides of the tail of the conical push rod and used for enabling the conical push rod to freely slide in a ball slideway.
The piezoresistive sensor is fixed on the T-shaped static iron core; the oil flows to form a pulse signal which acts on the piezoresistive sensor, the piezoresistive sensor transmits the pressure signal to the signal processing center, and the pressure signal is converted into a current signal after being processed, so that an error value is obtained. The electromagnetic attraction formula of the movable iron core:it can be seen that, when the air gap length delta, the movable iron core area S and the coil turns W are fixed, the current I can control the electromagnetic attraction force F, so that the moving position of the conical push rod is controlled to control the opening of the valve port, and the liquid flow rate is further controlled to compensate the error value.
The proportional throttle valve comprises a push rod B-1, a sealing ring B-2, a spring B-3 and a ball B-4; the ball is positioned at the tail part of the push rod, and the ball freely slides in the ball groove so as to enable the push rod to move; the head of the push rod is conical and used for controlling the opening of the valve port so as to regulate the oil flow at the valve port.
The concrete working process of the vertical hydraulic cylinder is as follows: when the working roller is subjected to vertical vibration, pressure is transmitted to the supporting seat, the supporting seat pushes the annular piston body to move in the outer cavity, the annular piston body drives the piston push rod in threaded connection with the annular piston body to move in the inner cavity, the magnetism of the permanent magnet piston is the same as that of the I-shaped iron core, and at the moment, the electromagnetic coil wound on the I-shaped iron core can form a magnetic field to generate a reaction magnetic force for the permanent magnet piston to realize primary vibration reduction. The distance change of the permanent magnet piston relative to the electromagnetic coil can cause the change of an intersecting magnetic field so as to generate a strain pulse signal which acts on the magnetostrictive displacement sensor to accurately measure the displacement of the permanent magnet piston, and further determine the vibration degree. The signal processing center converts the received displacement signal into a current signal so as to control the size of the magnetic field of the electromagnetic coil, thereby achieving the self-adaptive adjustment of the vibration condition; the change of the magnetic field of the electromagnetic coil can generate a changed magnetic force on the magnetic sliding block, so that oil in the cavity is pushed to flow, an oil pulse signal is generated at the piezoresistive sensor through the small opening, the signal processing center converts the received oil pressure signal into a current signal and feeds the current signal back to the electromagnetic induction coil, and the electromagnetic induction coil can control the displacement of the movable iron core according to the oil pressure so as to determine the displacement of the conical push rod. The ball rolls on the head of the conical push rod to push the push rod to move left and right so as to realize the proportional control of the opening of the valve port, thereby achieving the effect of secondary vibration reduction. The proportional electromagnet and the proportional throttle valve embedded in the cylinder body are symmetrically distributed on two sides, the taper angles of the left side and the right side of the conical push rod are opposite, the magnetic field generated by the electromagnetic coil drives the movable iron core to move downwards during oil storage, the left side conical push rod drives the left side push rod to move rightwards, the left side valve port opens oil liquid to enter the oil storage cavity for energy storage, and meanwhile the taper angle of the right side conical push rod is opposite to that of the left side so that the right side valve port is closed. When the oil in the oil storage cavity is released, the working principle is the same and the direction is opposite, at the moment, the left valve port is closed, and the right valve port is opened. In addition, when the annular piston body moves under vibration, the first check valve throttle valve and the second check valve embedded in the annular piston body change the hydraulic damping to realize further vibration reduction.
As shown in fig. 2 and 3, the magnetic sliding block and the inner cavity of the cylinder body form an adjustable oil storage cavity. When the lower working roller vibrates upwards, the supporting seat has upward pressure on the annular piston body, the annular piston body and the permanent magnet piston move upwards, and at the moment, the current in the electromagnetic coil increases the magnetic field to strengthen. The magnetism of the lower end of the magnetic sliding block is different from that of the upper end of the electromagnetic coil, the magnetic sliding block slides downwards under the action of a magnetic field, so that the volume of the oil storage cavity is increased, the oil in the outer cavity is stored, and the compression amount of the spring is large. When the lower working roller vibrates downwards, the annular piston body and the permanent magnet piston move downwards, the current in the electromagnetic coil reduces the magnetic field to weaken, and the magnetic sliding block moves upwards under the action of spring force, so that oil compensation is carried out on the rodless cavity.
As shown in fig. 4 and 5, a cross-sectional view and a partial enlarged view of the lateral cylinder are shown. The utility model takes the transverse hydraulic cylinder as a transverse vibration damper. The transverse hydraulic cylinder comprises a piston push rod 201, a screw 202, a sealing ring 203, a sealing ring 204, an end cover 205, a permanent magnet piston 206, a cavity iron core 207, a solenoid 208, a semiconductor cooling fin 209, an outer cylinder body 210, a third one-way throttle valve 211, a fourth one-way throttle valve 212 and a proportional throttle slide valve C.
The iron core with the cavity is fixed in the middle of the transverse hydraulic cylinder; the electromagnetic coil is wound on the iron core with the cavity, and 6 radiating semiconductor sheets which are uniformly distributed are arranged outside the electromagnetic coil; the third one-way throttle valve and the fourth one-way throttle valve are symmetrically embedded in the iron core with the cavity; the permanent magnet piston is internally embedded with a proportional electromagnet and a proportional throttle slide valve and is fixed on the piston push rod through a nut; the end cover is fixedly connected to the outer cylinder body through a screw and is in clearance fit with the piston push rod; and the inner ring and the outer ring of the end cover are respectively provided with a sealing ring for sealing the piston push rod and the outer cylinder body.
The proportional throttle slide valve comprises a spring C-1, a sealing ring C-2, a push rod C-3, a valve clack C-4, a spring C-5 and a T-shaped fixed block C-6; the ball is positioned at the tail part of the push rod, and the ball freely slides in the ball groove so as to enable the push rod to move; the push rod drives the valve clack to slide, so that the opening control of the valve port is realized, and the oil flow at the valve port is further controlled; a spring is fixed on the T-shaped fixed block and is used for resetting the valve clack. The other spring is fixed on the end of the push rod. The sealing ring is nested outside the push rod.
The specific working process of the transverse hydraulic cylinder is as follows: the working roller vibrates to enable the connecting rod to swing so as to push the piston rod push rod to move, the vibration is changed into transverse from vertical, when the pistons at two sides are close to the iron core with the cavity, current in the electromagnetic coil circumferentially wound on the iron core with the cavity is increased under the control of the signal processing center, and the magnetic field strength is enhanced so that the reaction force of the permanent magnet piston is increased, and therefore primary vibration reduction is achieved. The permanent magnet piston is internally embedded with a proportional electromagnet and a proportional throttle slide valve which are symmetrically distributed on the upper side and the lower side of the permanent magnet piston. When the permanent magnetic piston is close to the iron core with the cavity, oil enters the rod cavity from the rodless cavity, the lower side proportional electromagnetic valve drives the slide valve to move upwards, the lower side sliding valve port is opened, the valve port opening is transmitted to the proportional electromagnetic valve by the signal processing center to be controlled, the upper side valve clack is closed, and the oil enters the rod cavity, so that the two-stage hydraulic damping vibration attenuation is realized. Meanwhile, a third one-way throttle valve embedded in the cylinder body is opened, a fourth one-way throttle valve is closed, and part of rodless cavity oil is pressed into the cavity-containing iron core by the piston to store the oil; when the permanent magnet piston is far away from the iron core with the cavity, oil enters the rodless cavity from the rod cavity, the upper proportional electromagnetic valve drives the push rod to move downwards, the upper valve clack is opened, the lower valve clack is closed, and the oil enters the rodless cavity from the rod cavity, so that hydraulic damping vibration attenuation is realized. Meanwhile, a fourth one-way throttle valve embedded in the cylinder body is opened under the action of hydraulic pressure of oil in the cavity, and oil in the cavity enters the rodless cavity for oil compensation.
Furthermore, the vibration reduction frame is made of high damping materials and is used for assisting vibration reduction.
The utility model utilizes magnetic force and hydraulic damping to restrain vibration of a rolling mill roller system and a stand in a grading way, monitors vibration conditions in real time through a piezoresistive sensor and a magnetostrictive displacement sensor, processes pressure signals and displacement signals to obtain error values, adjusts electromagnetic output force by changing the current of an internal coil of an electromagnet, compensates the error values and further realizes proportion adjustment of magnetic force and hydraulic damping. The device has reasonable and simple structure and obvious vibration reduction effect.
When the two working rolls are subjected to vertical vibration, a magnetostrictive displacement sensor arranged on a permanent magnet piston in the inner cavity of the hydraulic cylinder receives signals and transmits the signals to a signal processing center, and the displacement signals are converted into current signals so as to control the magnetic field of an electromagnetic coil on the I-shaped iron core, further control the reaction force applied to the permanent magnet piston and realize primary vertical vibration inhibition; meanwhile, the magnetic sliding block fixedly connected to the I-shaped iron core through the spring pushes the inner cavity oil to move under the action of magnetic force, oil pulse is generated on the piezoresistive sensor, the piezoresistive sensor receives signals and transmits the signals to the signal processing center, the pressure signals are converted into current signals so as to control the displacement of the proportional electromagnet movable iron core, the proportional electromagnet movable electromagnetic valve is further regulated to further regulate the proportional electromagnetic throttle valve, the secondary damping generated by changing the opening of an oil valve port is used for inhibiting vertical vibration, and in addition, the magnetic sliding block and the lower cavity form an adjustable oil storage cavity, so that the energy storage and compensation of the oil in the outer cavity can be carried out in real time; the annular piston in the outer cavity is provided with a one-way throttle valve, so that the vertical vibration is inhibited in three stages.
When the working roll is in vertical vibration, the working roll supporting seat vibrates to drive the connecting rod to swing so that the permanent magnet piston rod moves in the cavity, the vibration is converted into transverse vibration from vertical, and the vibration is restrained in a grading manner by the electromagnetic coil, the proportional throttle valve and the vibration-damping frame, so that the vibration between the working roll and the frame is restrained.
The foregoing is only illustrative of the preferred embodiments and principles of the present utility model, and changes in specific embodiments will occur to those skilled in the art upon consideration of the teachings provided herein, and such changes are intended to be included within the scope of the utility model as defined by the claims.
Claims (7)
1. The grading vibration damper based on electromagnetic and hydraulic damping comprises a frame, a lower working roller arranged on the frame, and an upper working roller arranged above the lower working roller; the outer parts of the lower working roller and the upper working roller are respectively provided with a supporting seat; the device is characterized by also comprising a roller system damping device and a roller frame damping device;
the roller system vibration damping device is used for suppressing vibration among roller systems; the roller system vibration damper comprises four vertical hydraulic cylinders which are hinged between a supporting seat of an upper working roller and a supporting seat of a lower working roller;
the roller frame vibration damping device is used for suppressing vibration between the working roller and the frame; the roll stand vibration damping device comprises four transverse hydraulic cylinders, a connecting rod and a vibration damping stand; the connecting rod is used for connecting the supporting seat and the transverse hydraulic cylinder and converting the vertical vibration of the working roller into the axial movement of the piston of the hydraulic cylinder; the transverse hydraulic cylinder is fixed on the vibration reduction frame, and the vibration reduction frame is positioned on the frame;
the vertical hydraulic cylinders comprise a first end cover, a rubber gasket, a tensioning ring, a piston rod, a first one-way throttle valve, a second one-way throttle valve, an annular piston body, a permanent magnet piston, an I-shaped iron core, an electromagnetic coil, a spring, a magnetic sliding block, a magnetostrictive displacement sensor, a cylinder body, a proportional electromagnet and a proportional throttle valve;
the upper end surface of the permanent magnet piston is provided with a magnetostrictive displacement sensor which is fixedly connected to the piston rod through a nut; the electromagnetic coil is wound on the I-shaped iron core, the I-shaped iron core is fixed in the middle of the inner cavity of the vertical hydraulic cylinder, and the upper end of the I-shaped iron core is connected with the magnetic sliding block through a spring; the magnetic sliding block is circumferentially provided with a sealing ring for sealing external oil, and meanwhile, the variable volume formed by the magnetic sliding block and the inner cavity is used for compensating the oil in the inner cavity and the outer cavity of the hydraulic cylinder; the number of the proportion electromagnets is 2, and the proportion electromagnets and the proportion throttle valve are symmetrically embedded in the outer cavity; the first one-way throttle valve and the second one-way throttle valve are embedded in the annular piston body, and the two one-way conduction directions are opposite and are used for throttling oil return of a rod cavity in the outer cavity; the piston rod is in threaded connection with the annular piston body, and the bottom of the piston rod is also provided with a tensioning ring and a rubber gasket; the first end cover is fixedly connected to the cylinder body through a screw and is in clearance fit with the annular piston body; the inner ring and the outer ring of the first end cover are respectively provided with a sealing ring and an O-shaped sealing ring, and are used for sealing the annular piston body and the cylinder body;
the 2 proportion electromagnets comprise 2 conical push rods, balls, ball slide ways, movable iron cores, springs, T-shaped static iron cores, piezoresistive sensors and electromagnetic coils; the T-shaped static iron core is wound with an electromagnetic coil and is connected with the movable iron core through a spring; the movable iron core is in interference fit with the tapered push rods, the top ends of the 2 tapered push rods are designed into slideways with opposite taper and are provided with ball grooves, and balls are arranged at two sides of the cross-shaped design of the tail part of the tapered push rod and used for enabling the tapered push rods to freely slide in the ball slideways;
the magnetostrictive displacement sensor and the proportional electromagnet form electromagnetic compensation primary vibration reduction; the piezoresistive sensor and the proportional throttle valve return oil and discharge oil to the inner cavity and the outer cavity to form proportional throttle type secondary vibration reduction; the one-way throttle valve in the outer cavity returns oil to the rod cavity of the hydraulic cylinder to form the hydraulic damping three-stage vibration reduction.
2. The stepped vibration damping device based on electromagnetic and hydraulic damping according to claim 1, wherein said piezoresistive sensor is fixed on a T-shaped static core; the magnetic sliding block drives the oil in the inner cavity to flow to form a pulse signal which acts on the piezoresistive sensor, the piezoresistive sensor transmits the pressure signal to the signal processing center, the pressure signal is converted into a current signal after being processed to obtain an error value, and the current of the proportional electromagnet coil is adjusted according to the error value to control the opening of the valve port of the proportional throttle valve, so that error value compensation is realized.
3. The staged damping device based on electromagnetic and hydraulic damping as defined in claim 1, wherein the 2 proportional throttle valves include a first pushrod, a sealing ring, a spring, a first ball; the first ball is positioned at the tail part of the push rod, and freely slides in the ball groove so as to enable the first push rod to move; the first push rod head is conical and used for controlling the opening of the valve port so as to regulate the oil flow at the valve port.
4. The grading vibration damper based on electromagnetic and hydraulic damping according to claim 1, wherein the conical slide way at the top end of the conical push rod in the 2 proportional electromagnets acts on the proportional throttle push rod, and the two symmetrically arranged conical slide ways are opposite in direction, so that the 2 proportional throttle valves are in opposite one-way conduction directions to respectively conduct proportional throttling on oil outlet compensation and oil return compensation of the inner cavity and the outer cavity.
5. A staged damping device as defined in claim 3, wherein the lateral hydraulic cylinder includes a piston pushrod, screw, seal ring, second end cap, permanent magnet piston, chambered core, solenoid, semiconductor fin, outer cylinder, third one-way throttle valve, fourth one-way throttle valve and proportional throttle spool;
the iron core with the cavity is fixed in the middle of the transverse hydraulic cylinder; the electromagnetic coil is wound on the iron core with the cavity, and 6 semiconductor cooling fins which are uniformly distributed are arranged outside the electromagnetic coil; the third one-way throttle valve and the fourth one-way throttle valve are symmetrically embedded in the iron core with the cavity; the permanent magnet piston is internally embedded with a proportional electromagnet and a proportional throttle slide valve and is fixed on the piston push rod through a nut; the second end cover is fixedly connected to the outer cylinder body through a screw and is in clearance fit with the piston push rod; and the inner ring and the outer ring of the second end cover are respectively provided with a sealing ring for sealing the piston push rod and the outer cylinder body.
6. The staged damping device based on electromagnetic and hydraulic damping as defined in claim 5, wherein the proportional throttle spool includes a spring, a second pushrod, a valve flap and a T-shaped fixed block; the tail part of the second push rod is provided with a second ball which freely slides in the ball groove so as to enable the second push rod to move; the second push rod drives the valve clack to slide, so that the opening control of the valve port is realized, and the oil flow at the valve port is further controlled; the spring is fixed on the T-shaped fixed block and is used for resetting the valve clack.
7. The device according to any one of claims 1-6, characterized in that the vibration-damping frame is made of a high damping material.
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2016074109A1 (en) * | 2014-11-13 | 2016-05-19 | 哈尔滨工程大学 | Composite magnetic circuit double-permanent magnet electromagnet and composite magnetic circuit double-permanent magnet high-speed solenoid valve |
| CN107419663A (en) * | 2017-05-20 | 2017-12-01 | 董英山 | A kind of bridge construction damping device |
| CN109114149A (en) * | 2018-09-12 | 2019-01-01 | 杭州电子科技大学 | A kind of milling train classification damping device |
| CN215596935U (en) * | 2021-05-14 | 2022-01-21 | 郑州万祥电力工程有限公司 | Electric power facility shock attenuation platform |
| CN114160582A (en) * | 2021-11-19 | 2022-03-11 | 太原理工大学 | Hydraulic vibration suppression device for vertical vibration of rolling mill |
-
2022
- 2022-07-13 CN CN202210825885.3A patent/CN115059729B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2016074109A1 (en) * | 2014-11-13 | 2016-05-19 | 哈尔滨工程大学 | Composite magnetic circuit double-permanent magnet electromagnet and composite magnetic circuit double-permanent magnet high-speed solenoid valve |
| CN107419663A (en) * | 2017-05-20 | 2017-12-01 | 董英山 | A kind of bridge construction damping device |
| CN109114149A (en) * | 2018-09-12 | 2019-01-01 | 杭州电子科技大学 | A kind of milling train classification damping device |
| CN215596935U (en) * | 2021-05-14 | 2022-01-21 | 郑州万祥电力工程有限公司 | Electric power facility shock attenuation platform |
| CN114160582A (en) * | 2021-11-19 | 2022-03-11 | 太原理工大学 | Hydraulic vibration suppression device for vertical vibration of rolling mill |
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