A variable roll diameter tension adjustment device based on a high-speed switching valve

Abstract

The present invention discloses a variable roll diameter tension adjusting device based on a high-speed switching valve, which comprises a variable roll diameter mechanism. The variable roll diameter mechanism includes a roll shaft, a first component and a second component. The first component and the second component are symmetrically arranged on both sides of the middle surface of the roll shaft, and the positions between the first component and the second component are rotationally misaligned by 45°. The first component and the second component respectively include a radially telescopic hydraulic cylinder and a convex-shaped roll lobe, and the convex-shaped roll lobe is located above the radially telescopic hydraulic cylinder. The present invention uses a variable roll diameter tension roll to replace the traditional tension adjusting method of driving the tension roll to lift by a hydraulic cylinder, avoiding the problems of large tension fluctuations and strip running deviation caused by the inclination of the tension roll. The present invention adopts a low-cost high-speed valve group to perform closed-loop control on the roll diameter of the tension roll through PWM control (a technology for modulating the width of pulses), so as to realize real-time dynamic adjustment of the strip tension. The device is simple and efficient, and has high economic benefits.

Description

Technical Field

[0001] The present invention belongs to the field of rolling technology equipment, and particularly relates to a variable roll diameter tension regulating device based on a high-speed switching valve. Background Art

[0002] Strip steel is a narrow and long steel plate produced by various rolling enterprises to meet the needs of different industrial sectors for industrial production of various metals or mechanical products. Rolling is an indispensable part of the strip steel production process. High-speed continuous rolling improves the production efficiency of strip steel.

[0003] The three-roll tension roll group is widely used in the high-speed continuous rolling production line of strip steel. The traditional three-roll tension roll group consists of two fixed pressing rolls and a tension roll that can move up and down in the vertical direction. The tension roll is driven by hydraulic cylinders on both sides in the vertical direction to change the wrap angle of the strip steel around the tension roll, further change the friction force at the wrap contact (i.e., the wrap angle), and then change the tension value of the strip steel at the inlet or outlet of the tension roll, so as to achieve tension control for the unit. However, in this process, it is very difficult for the hydraulic cylinders on both sides of the tension roll to move at the same speed, which will cause the problems of the tension roll tilting, large tension fluctuations, and strip steel deviation. Summary of the Invention

[0004] In order to overcome the existing technical problems, the present invention provides a variable roll diameter tension regulating device based on a high-speed switching valve, which can solve the problems of large tension fluctuations and strip steel deviation caused by the tilting of the tension roll.

[0005] The above technical object of the present invention is achieved through the following technical solutions:

[0006] A variable roll diameter tension regulating device based on a high-speed switching valve, including a variable roll diameter mechanism. The variable roll diameter mechanism includes a roll shaft, a first component, and a second component. The first component and the second component are symmetrically arranged on both sides of the middle plane of the roll shaft, and the positions of the first component and the second component are rotationally misaligned by 45°; the first component and the second component respectively include a radially telescopic hydraulic cylinder and a convex-shaped roller lobe, and the convex-shaped roller lobe is located above the radially telescopic hydraulic cylinder.

[0007] Further setting, the radially telescopic hydraulic cylinders and the convex-shaped roller lobes are circumferentially evenly distributed.

[0008] Further setting, there are four sets of the radially telescopic hydraulic cylinders and the convex-shaped roller lobes.

[0009] Further setting, a pressure sensor is arranged inside the convex-shaped roller lobe. Further setting, five groups of slide rails are arranged on the inner side of the convex-shaped roller lobe.

[0010] Further setting: The variable roll diameter tension regulating device based on the high-speed switching valve further includes a fan slot compensation mechanism and a slider. The fan slot compensation mechanism is fixedly connected to the slider and can slide on the inner rail of the roll lobe. The slider is installed on the said rail.

[0011] Further setting: There are two groups of cylindrical grooves on the roll shaft. One group is located on the left side of the middle plane of the roll shaft, and the other group is located on the right side of the middle plane. Each group of cylindrical grooves is evenly distributed circumferentially. The two groups of cylindrical grooves are symmetrically arranged on both sides of the roll shaft and rotated and displaced by 45°. The radial telescopic hydraulic cylinder is in interference fit with the cylindrical groove and can be used for rapid radial expansion and contraction of the convex roll lobe, so as to realize variable roll diameter adjustment; the roll shaft is driven by a motor to realize circumferential rotation, and the real-time rotation speed is adjustable. Further setting: Each group of cylindrical grooves has four.

[0012] Further setting: The radial telescopic hydraulic cylinder includes a push rod, a first sealing ring, an end cover, an outer cylinder body, a second sealing ring, a piston, a displacement sensor, a nut, and a high-speed switching valve. The top of the push rod is threadedly connected to the piston, and the tail of the push rod is fixed to the convex-shaped roll lobe. The piston is located in the cavity of the outer cylinder body. A second sealing ring is provided circumferentially on the piston to seal the internal oil of the cavity. The nut is fixed to the top of the push rod to limit and lock the piston. The displacement sensor is embedded in the top of the push rod. Four high-speed switching valves are embedded in the center of the outer cylinder body and symmetrically arranged, which are used to regulate the oil pressure difference between the rodless cavity and the rodless cavity to control the telescopic displacement of the piston, so as to realize the roll diameter adjustment action. The end cover is fixedly connected to the outer cylinder body, and a first sealing ring is provided on the end cover to seal the end cover. The displacement sensor and the high-speed switching valve are combined to control, which can be used for feedback adjustment of the displacement of the push rod in the radial telescopic hydraulic cylinder to ensure the synchronization of the radial movement of the eight convex-shaped roll lobes.

[0013] Further setting: The high-speed switching valve includes a housing, a first electromagnetic coil, a first spring, a convex block, a valve core push rod, a sealing ring, a valve body, a first oil hole, a ball core, a filter screen, a plug block, a second spring, a sealing cover, a second oil hole, and a guide block. The first electromagnetic coil is fixed in the housing. The upper end of the convex block is limited and installed with the housing through the first spring. The lower end of the convex block is threadedly connected to the valve core push rod. The guide block is fixed in the valve body to guide the valve core push rod. The sealing ring is fixed inside the guide block to seal the circumference of the push rod. The ball core is arranged at the end of the valve core push rod, and a filter screen is provided circumferentially on the ball core. The second spring is fixed on the plug block to reset the ball core. The plug block is arranged on the sealing cover. The sealing cover is in interference fit with the said outer cylinder body and combines with the plug block to double-seal the oil. The first oil hole and the second oil hole are arranged on both sides of the valve body to adjust the oil pressure in the cavity. Further setting: The high-speed switching valve controls the on-off time of the valve by controlling the duty cycle, so as to realize the adjustment of the flow rate. The duty cycle is defined as: The value range is -0.5 < τ < 0.5, where r is the set value of the radius of the tension roller, r2 is the actual radius of the tension roller. The larger the absolute value of the duty cycle, the greater the flow rate through the valve port, and the faster the piston runs. The convex-shaped roller petals are fixed on the push rod of the radial telescopic hydraulic cylinder and arranged circumferentially in a staggered manner. When the tension roller rotates at a high speed, the adjacent roller petals are quickly compensated alternately, which is beneficial to the periodic staggered contact between the strip steel and the roller petals, making the load on the roller petals uniform and reducing the tension fluctuation. There are a total of eight fan gap compensation mechanisms, which are respectively located between the convex-shaped roller petals and can be used for adaptive compensation of the fan gap change, so as to control the fan gap within the error range, further control the contact area between the strip steel and the fan gap of the tension roller, and reduce the tension fluctuation caused by the gap.

[0014] Furthermore, the fan gap compensation mechanism includes a cavity-containing long table, a first piston rod, a third spring, a second piston rod, a slideway, a slide block, a first semi-cylindrical body, a hydraulic outer cylinder, a first push rod, a second electromagnetic coil, a first electromagnetic reversing valve, a second electromagnetic reversing valve, a fourth spring, a metal piston, a third piston rod, a fourth piston rod, a second semi-cylindrical body, a convex platform, a first oil passage, a second oil passage, and a third oil passage. There are two groups of convex platforms on the cavity-containing long table, and the two groups of convex platforms are symmetrically arranged. Each group contains five convex platforms. There are two symmetric cylindrical cavities on the upper part of the convex platform, and they are connected to the cylindrical cavities at the lower part of the convex platform through the second oil passage and the third oil passage. The first piston rod and the third piston rod are symmetrically installed in the cylindrical cavities at the lower part of the convex platform, and the second piston rod and the fourth piston rod are arranged in the symmetrically arranged upper cavities. The third spring is used to reset the piston rod. The slideways are symmetrically fixed above the convex platform. The slide block is fixedly connected to the second piston rod and the fourth piston rod, and the slide block can be pushed by the piston rod to move horizontally on the slideway. The first semi-cylindrical body and the second semi-cylindrical body are in interference fit with the slide block and are used for micro-compensation of the fan gap. There are a total of five hydraulic outer cylinders, and the hydraulic outer cylinders are in interference fit with the cavity-containing long table. The metal piston is arranged in the hydraulic outer cylinder, and the metal piston is connected to the first push rod and fixed by a nut. The second electromagnetic coil is embedded in the hydraulic outer cylinder. When energized, it generates an attractive force on the metal piston to push the first push rod to move and compress the fourth spring, thereby promoting the cavity-containing long table to move in the vertical direction. The upper end of the first push rod is fixedly connected to the convex-shaped roller petal. The fourth spring is used to reset the piston. The first oil passage is respectively communicated with the external oil tank and the rodless cavity of the hydraulic outer cylinder through the first electromagnetic reversing valve and the second electromagnetic reversing valve, and can be used for supplying oil and discharging oil to the rodless cavity of the lower cavity of the cavity-containing long table.

[0015] Furthermore, the slider is respectively fixedly connected to the first piston rod and the third piston rod and can slide on the inner slide rail of the roller petal. The slider is installed on the slide rail.

[0016] In summary, the present invention has the following beneficial effects:

[0017] 1. The present invention uses a variable roll diameter tension roll to replace the traditional tension adjustment method of driving the tension roll to lift by a hydraulic cylinder, avoiding the problems of large tension fluctuations and strip deviation caused by the inclination of the tension roll.

[0018] 2. The present invention uses a low-cost high-speed valve group to perform closed-loop control on the roll diameter of the tension roll through PWM control (a technology for modulating the width of pulses), thereby realizing real-time dynamic adjustment of strip tension. The device is simple and efficient, with high economic benefits. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 is a schematic structural diagram of a variable roll diameter tension adjustment device based on high-speed on-off valves in a preferred embodiment;

[0020] Figure 2 is Figure 1 the schematic structural diagram of the H-H cross-section in

[0021] Figure 3 is a schematic structural diagram of the roll shaft of a variable roll diameter tension adjustment device based on high-speed on-off valves in a preferred embodiment;

[0022] Figure 4 is a schematic cross-sectional structure diagram of a radial telescopic hydraulic cylinder;

[0023] Figure 5 is a schematic cross-sectional structure diagram of a high-speed on-off valve;

[0024] Figure 6 is a schematic structural diagram of a fan-shaped gap compensation mechanism under small tension fluctuations;

[0025] Figure 7 is a schematic structural diagram of a fan-shaped gap compensation mechanism under large tension fluctuations;

[0026] Figure 8 is Figure 6 the side view of the I-I plane in

[0027] Figure 9 is Figure 8 the enlarged view at J in

[0028] Figure 10 is the schematic diagram of tension adjustment principle during cold tandem rolling.

[0029] Reference numerals: 1, roller shaft; 2, radially telescopic hydraulic cylinder; 20, push rod; 21, first sealing ring; 22, end cover; 23, outer cylinder body; 24, second sealing ring; 25, piston; 26, displacement sensor; 27, nut; 28, high-speed switching valve; 281, first high-speed switching valve; 282, second high-speed switching valve; 283, third high-speed switching valve; 284, fourth high-speed switching valve; 2801, housing; 2802, first electromagnetic coil; 2803, first spring; 2804, convex block; 2805, spool push rod; 2806, sealing ring; 2807, valve body; 2808, first oil hole; 2809, ball core; 2810, filter screen; 2811, plug; 2812, second spring; 2813, sealing cover; 2814, second oil hole; 2815, guide block; 3, convex-shaped roller lobe; 301, cavity-bearing long platform; 302, first piston rod; 303, third spring; 304, second piston rod; 305, slideway; 306, slide block; 307, first semi-cylinder; 308, hydraulic outer cylinder body; 309, first push rod; 310, second electromagnetic coil; 311, first electromagnetic reversing valve; 312, second electromagnetic reversing valve; 313, fourth spring; 314, metal piston; 315, third piston rod; 316, fourth piston rod; 317, second semi-cylinder; 318, convex platform; 319, first oil passage; 320, second oil passage; 321, third oil passage; 4, pressure sensor; 5, slide rail; 6, slider. Detailed implementation manners

[0030] To more clearly illustrate the embodiments of the present invention, the following will describe the specific implementation manners of the present invention with reference to the accompanying drawings. Obviously, the accompanying drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on these drawings, and other implementation manners can also be obtained.

[0031] As Figure 1 、 Figure 2 shown, the preferred embodiment of the variable roller diameter tension adjusting device based on a high-speed switching valve includes a variable roller diameter mechanism. The variable roller diameter mechanism includes a roller shaft 1, a first component, and a second component. The first component and the second component are symmetrically arranged on both sides of the middle surface of the roller shaft 1, and the positions between the first component and the second component are rotationally misaligned by 45°. The first component and the second component respectively include a radially telescopic hydraulic cylinder 2 and a convex-shaped roller lobe 3. The convex-shaped roller lobe 3 is located above the radially telescopic hydraulic cylinder 2. There are four sets of radially telescopic hydraulic cylinders 2 and convex-shaped roller lobes 3 evenly distributed circumferentially. A pressure sensor 4 is provided inside the convex-shaped roller lobe 3, and five sets of slide rails 5 are provided on the inner side of the convex-shaped roller lobe 3. It also includes a fan gap compensation mechanism and a slider 6. The fan gap compensation mechanism is fixedly connected to the slider 6, and the slider 6 is installed on the slide rail 5.

[0032] As Figure 3As shown in the figure, there are two groups of cylindrical grooves on the roller shaft 1. One group is located on the left side of the middle plane of the roller shaft 1, and the other group is located on the right side of the middle plane of the roller shaft 1. There are four cylindrical grooves evenly distributed in the circumferential direction in each group. The two groups of cylindrical grooves are symmetrically arranged on both sides of the middle plane of the roller shaft 1 and are rotationally misaligned by 45°. The radially telescopic hydraulic cylinder 2 is in interference fit with the cylindrical groove and can be used for rapid radial expansion and contraction of the convex roller lobe, so as to realize the variable roller diameter adjustment. The convex-shaped roller lobe 3 is fixed above eight radially telescopic hydraulic cylinders 2 installed in a staggered manner and arranged circumferentially in a staggered manner, which can be used for periodic compensation of the roller diameter change. A slide rail 5 is provided on the inner side of the roller lobe.

[0033] As Figure 4 shown in the figure, the radially telescopic hydraulic cylinder 2 includes a push rod 20, a first sealing ring 21, an end cover 22, an outer cylinder body 23, a second sealing ring 24, a piston 25, a displacement sensor 26, a nut 27, and a high-speed switching valve 28. The top of the push rod 20 is threadedly connected to the piston 25, and the tail end of the push rod 20 is fixedly connected to the convex-shaped roller lobe 3. The piston 25 is located in the cavity of the outer cylinder body 23. A second sealing ring 24 is provided on the circumference of the piston 25. The nut 27 is fixed to the top of the push rod 20 for self-locking the piston in position. The displacement sensor 26 is embedded in the top of the push rod 20 for monitoring the piston displacement. Four high-speed switching valves 28 are embedded in the outer cylinder body 23 and are arranged symmetrically about the center for regulating the oil pressure difference between the rodless cavity and the rod cavity to control the telescopic displacement amount of the piston, so as to realize the roller diameter adjustment action. The end cover 22 is fixedly connected to the outer cylinder body 23, and a first sealing ring 21 is provided on the end cover 22 for sealing the end cover 22.

[0034] As Figure 5 shown in the figure, the high-speed switching valve 28 includes a housing 2801, a first electromagnetic coil 2802, a first spring 2803, a convex block 2804, a valve core push rod 2805, a sealing ring 2806, a valve body 2807, a first oil hole 2808, a ball core 2809, a filter screen 2810, a plug block 2811, a second spring 2812, a sealing cover 2813, a second oil hole 2814, and a guide block 2815. The first electromagnetic coil 2802 is fixed in the housing 2801. The upper end of the convex block 2804 is installed in a limited position with the housing 2801 through the first spring 2803. The lower end of the convex block 2804 is threadedly connected to the valve core push rod 2805. The guide block 2815 is fixed in the valve body 2807. The sealing ring 2806 is fixed inside the guide block 2815. The ball core 2809 is arranged at the end of the valve core push rod 2805. A filter screen 2801 is provided on the circumference of the ball core 2809. The second spring 2812 is fixed on the plug block 2811 for resetting the ball core 2809. The plug block 2811 is arranged on the sealing cover 2813. The sealing cover 2813 is in interference fit with the outer cylinder body 23 and is combined with the plug block 2811 to double-seal the oil. The first oil hole 2808 and the second oil hole 2814 are arranged on both sides of the valve body 2807 for adjusting the oil pressure in the cavity.

[0035] As shown Figures 6 - 8 in the figure, the fan slot compensation mechanism includes a cavity - length platform 301, a first piston rod 302, a third spring 303, a second piston rod 304, a slideway 305, a slide block 306, a first semi - cylinder 307, a hydraulic outer cylinder 308, a first push rod 309, a second electromagnetic coil 310, a first electromagnetic reversing valve 311, a second electromagnetic reversing valve 312, a fourth spring 313, a metal piston 314, a third piston rod 315, a fourth piston rod 316, a second semi - cylinder 317, a convex platform 318, a first oil passage 319, a second oil passage 320, and a third oil passage 321. There are two groups of convex platforms 318 on the cavity - length platform 301. The two groups of convex platforms 318 are symmetrically arranged, and each group contains five convex platforms 318. There are two symmetric cylindrical cavities on the upper part of the convex platform 318, and they are connected to the cylindrical cavity at the lower part of the convex platform 318 through the second oil passage 320 and the third oil passage 321. The first piston rod 302 and the third piston rod 315 are symmetrically installed in the cylindrical cavity at the lower part of the convex platform 318. The second piston rod 304 and the fourth piston rod 316 are arranged in the symmetrically - arranged upper cavity. The third spring 303 is used to reset the piston rod. The slideways 305 are symmetrically fixed on the upper part of the cavity - length platform 301. The slide block 306 is fixedly connected to the second piston rod 304 and the fourth piston rod 316. The first semi - cylinder 307 and the second semi - cylinder 317 are in interference fit with the slide block 306 and are used for micro - compensating the fan slot. The piston rod pushes the slide block 306 to move horizontally on the slideway 305. The hydraulic outer cylinder 308 is in interference fit with the cavity - length platform 301. The metal piston 314 is arranged in the hydraulic outer cylinder 308. The metal piston 314 is connected to the push rod 309 and fixed by a nut. The second electromagnetic coil 310 is embedded in the hydraulic outer cylinder 308. When the second electromagnetic coil 310 is energized, it will generate an attractive force on the metal piston, thereby pushing the first push rod 309 to move and compress the spring 313, and further promoting the cavity - length platform 301 to move in the vertical direction. The upper end of the first push rod 309 is fixedly connected to the convex - shaped roller lobe 3. The first oil passage 319 is respectively communicated with the external oil tank and the rodless cavity of the hydraulic outer cylinder 308 through the first electromagnetic reversing valve 311 and the second electromagnetic reversing valve 312, and is used for supplying oil and discharging oil to the rodless cavity of the lower cavity of the cavity - length platform 301. The fourth spring 313 is fixedly connected to the metal piston 314. Both the first electromagnetic reversing valve 311 and the second electromagnetic reversing valve 312 are two - position three - way electromagnetic reversing valves, which can be used to control the liquid flow direction. The first piston rod 302 and the third piston rod 315 are installed in the lower cavity of the cavity - length platform 301 and can be used for adaptively adjusting the change of the fan slot gap in the horizontal direction. The slider 6 is respectively fixedly connected to the first piston rod 302 and the third piston rod 315 and can be used to assist the cavity - length platform 301 to move in the vertical direction to adapt to the change of the fan slot gap in the vertical direction.

[0036] As shown Figure 10As shown, two pressing rollers with equal diameters and a tension roller with variable diameter form a tension adjustment system. The two pressing rollers are symmetrically arranged on both sides of the tension roller. When the positions of the three rollers are fixed, It can be seen that when the Q measured by the pressure sensor is constant, the actual tension value T depends on the wrap angle θ produced by the strip on the tension roller. The change in the wrap angle θ depends on the change in the roller diameter r2 of the tension roller. By establishing the following geometric relationship model:

[0037] 2α+2β+θ=2π; it can be deduced that

[0038] L1 - the horizontal distance between the pressure roller and the tension roller center, which is a fixed value;

[0039] L2 - the vertical distance between the pressure roller and the tension roller center, which is a fixed value;

[0040] r1——the radius of the pressure roller, which is a fixed value;

[0041] r2——the actual radius of the variable roller tension roller E, which is a variable;

[0042] A, F - roller cores of two pressing rollers;

[0043] E——roller center of tension roller;

[0044] B - the point of tangency between the strip and the pinch roller A at the exit;

[0045] D - the tangent point between the strip and the tension roller E at the entrance;

[0046] C - the intersection of the line connecting the roller centers of the pressure roller A and the tension roller E and the line connecting the tangent points B and D;

[0047] L AC ——the distance between ACs;

[0048] L CE ——Distance between CEs;

[0049] α——the angle between the line connecting the centers of the pressure roller and the tension roller and the vertical direction;

[0050] β - the angle between the line connecting the centers of the pressure roller and the tension roller and the radius of the tangent point of the strip on the tension roller;

[0051] The diameter of the tension roller can be controlled by adjusting the action of the radial telescopic hydraulic cylinder 2 in the roller diameter variable mechanism. The roller diameter and the wrap angle θ form an inverse cosine function, which further realizes the control of the wrap angle, thereby adjusting the actual tension.

[0052] The working process of the roller diameter changing mechanism of the preferred embodiment is as follows:

[0053] like Figure 4, 5 As shown, the four high-speed switching valves 28 embedded in the outer cylinder can control the oil pressure in the rod chamber and the rodless chamber in real time, enabling the piston to move rapidly in the cavity, thereby driving the radially moving convex roller lobe 3 fixedly connected to the push rod 20; the four high-speed switching valves 28 control the on-off time of the valves by controlling the duty cycle, thereby achieving flow regulation. The duty cycle is defined as: The value range is -0.5 < τ < 0.5, where r is the set value of the tension roller radius and r2 is the actual radius of the tension roller. The larger the absolute value of the duty cycle, the greater the flow rate through the valve port and the faster the piston runs; if -0.5 < τ < 0, the actual wrap angle is less than the set value, that is, the actual tension value T is less than the theoretical set value T0. The second high-speed switching valve 282 and the fourth high-speed switching valve 284 work, and the first high-speed switching valve 281 and the third high-speed switching valve 283 are closed. Among them, the first electromagnetic coil 2802 in the fourth high-speed switching valve 284 is energized, and the generated magnetic force pushes the convex block 2804 to drive the valve core push rod 2805 to push open the ball center 2809 and compress the second spring 2812, so that the external high-pressure oil enters the rodless chamber from the first oil hole 2808 through the second oil hole 2814, pushing the piston to compress the oil in the rod chamber. At the same time, the second high-speed switching valve 282 opens in the same form, allowing the oil in the rod chamber to flow quickly into the fuel tank until the duty cycle increases to zero. The first electromagnetic coils 2802 of the second high-speed switching valve 282 and the fourth high-speed switching valve 284 are de-energized, and the second spring 2812 resets to block the ball center 2809 to block the oil port, and the valve port is closed, and the rod chamber and the rodless chamber reach the pressure-holding state. During this process, the actual roller diameter r2 will quickly increase to the set value r and then remain unchanged, and the wrap angle θ increases as the roller diameter increases, so that the actual tension T increases to the theoretical set value T0 and remains constant; if 0 < τ < 0.5, the actual wrap angle is greater than the set value, that is, the actual tension value T is greater than the theoretical set value T0. The first high-speed switching valve 281 and the third high-speed switching valve 283 are opened, and the second high-speed switching valve 282 and the fourth high-speed switching valve 284 are closed until the duty cycle decreases to zero. During this process, the actual roller diameter r2 will quickly decrease to the set value r and then remain unchanged, and the wrap angle θ decreases as the roller diameter decreases, so that the actual tension T decreases to the theoretical set value T0 and remains constant.

[0054] Working principle of the fan gap compensation mechanism:

[0055] As Figure 6 shown, for the high-speed rotating tension roller, when there is a small tension fluctuation in the strip, the change in the roller diameter is small, and the change in the fan gap is within the allowable error range. Therefore, the small change in the fan gap caused by the change in the roller diameter has too little impact on the tension fluctuation and can be ignored.

[0056] As Figure 7As shown, when there is a large tension fluctuation in the strip, the change in roll diameter is relatively large. At this time, the change in the fan slot gap is also relatively large, and the fan slot gap needs to be compensated to keep the gap within the allowable error range.

[0057] The specific working process of the preferred embodiment is as follows:

[0058] When the roll diameter increases from small to large, the fan slot extends from the Figure 6 state to the Figure 7 state. The fan slot gap gradually expands from the initial state. At this time, the first electromagnetic directional valve 311 is opened, and the high-pressure oil in the oil tank enters the rodless cavity in the lower cavity of the belt cavity long table 301 through the first electromagnetic directional valve 311 and the first oil passage 319, thereby pushing the first piston rod 302 and the third piston rod 315 to move to both sides. As a result, the oil in the rod cavity is compressed and flows through the second oil passage 320 and the third oil passage 321 into the symmetrically arranged upper cavity, further pushing the second piston rod 304 and the fourth piston rod 316 in the upper cavity to move to both sides and simultaneously compressing the third spring 303. Then, it drives the slide table 306 to move on the slideway 305, causing the first semi-cylinder 307 and the second semi-cylinder 317 fixed on the slide table 306 to move towards both sides of the fan slot.

[0059] When the fan slot continues to expand until the first piston rod 302 and the third piston rod 315 in the lower cavity of the belt cavity long table 301 move to both sides exceeding of the total stroke of the lower cavity, the first electromagnetic directional valve 311 is closed, and the second electromagnetic directional valve 312 is opened. At this time, a pressure difference will be formed between the lower cavity of the belt cavity long table 301 and the rodless cavity in the hydraulic outer cylinder 308. The compressed fourth spring 313 will stretch and push the metal piston 314 to compress the oil in the rodless cavity and enter the belt cavity long table 301 through the first oil passage 319 for oil compensation, so that the first piston rod 302 and the third piston rod 315 move to both sides. The second piston rod 304 and the fourth piston rod 316 continue to move to both sides under the action of the oil pressure difference. At the same time, the reset of the compressed fourth spring 313 will cause the belt cavity long table 301 fixedly connected to the hydraulic outer cylinder 308 to move vertically upward, enabling the first semi-cylinder 307 and the second semi-cylinder to cooperate with the staggered convex-shaped roller petals 3 to compensate for the fan slot gap, as shown in Figure 7 .

[0060] The above embodiments are only explanations of the present invention, and they do not limit the present invention. After reading this specification, those skilled in the art can make modifications without creative contributions to this embodiment as needed, but as long as they are within the scope of the claims of the present invention, they are protected by the patent law.

Claims

1. A variable roll diameter tension adjusting device based on a high-speed switching valve, characterized in that It includes a variable roll diameter mechanism, and the variable roll diameter mechanism includes a roll shaft (1), a first component, and a second component. The first component and the second component are symmetrically arranged on both sides of the middle plane of the roll shaft (1), and the positions between the first component and the second component are rotationally misaligned by 45°; the first component and the second component respectively include a radially telescopic hydraulic cylinder (2) and a convex-shaped roll lobe (3), and the convex-shaped roll lobe (3) is located above the radially telescopic hydraulic cylinder (2). The variable roll diameter tension regulating device based on a high-speed switching valve further includes a fan-shaped gap compensation mechanism and a slider (6). The fan-shaped gap compensation mechanism is fixedly connected to the slider (6), and the slider (6) is installed on a slide rail (5). The fan-shaped gap compensation mechanism includes a cavity-containing long table (301), a first piston rod (302), a third spring (303), a second piston rod (304), a slideway (305), a slide table (306), a first semi-cylinder (307), a hydraulic outer cylinder (308), a first push rod (309), a second electromagnetic coil (310), a first electromagnetic reversing valve (311), a second electromagnetic reversing valve (312), a fourth spring (313), a metal piston (314), a third piston rod (315), a fourth piston rod (316), a second semi-cylinder (317), a convex platform (318), a first oil passage (319), a second oil passage (320), and a third oil passage (321). Two groups of convex platforms (318) are provided on the cavity-containing long table (301), and the two groups of convex platforms (318) are symmetrically arranged. Two symmetric cylindrical cavities are provided on the upper part of the convex platform (318) and are connected to the cylindrical cavities in the lower part of the convex platform (318) through the second oil passage (320) and the third oil passage (321). The first piston rod (302) and the third piston rod (315) are symmetrically installed in the cylindrical cavities in the lower part of the convex platform (318). The second piston rod (304) and the fourth piston rod (316) are arranged in the symmetrically arranged upper cavities. The slideway (305) is symmetrically fixed on the upper part of the cavity-containing long table (301). The slide table (306) is fixedly connected to the second piston rod (304) and the fourth piston rod (316). The first semi-cylinder (307) and the second semi-cylinder (317) are in interference fit with the slide table (306). The hydraulic outer cylinder (308) is in interference fit with the cavity-containing long table (301). The metal piston (314) is arranged in the hydraulic outer cylinder (308). The metal piston (314) is connected to the push rod (309). The second electromagnetic coil (310) is embedded in the hydraulic outer cylinder (308). The upper end of the first push rod (309) is fixedly connected to the convex-shaped roll lobe (3). The first oil passage (319) is respectively communicated with an external oil tank and the rodless cavity of the hydraulic outer cylinder (308) through the first electromagnetic reversing valve (311) and the second electromagnetic reversing valve (312). The fourth spring (313) is fixedly connected to the metal piston (314). The slider (6) is respectively fixedly connected to the first piston rod (302) and the third piston rod (315).

2. The variable roll diameter tension adjusting device based on a high-speed switching valve according to claim 1, characterized in that The radially telescopic hydraulic cylinders (2) and the convex-shaped roll lobes (3) are circumferentially and evenly distributed.

3. The variable roll diameter tension regulating device based on a high-speed on-off valve according to claim 2, wherein, There are four sets of the described radial telescopic hydraulic cylinders (2) and the convex-shaped roller petals (3).

4. The variable roll diameter tension adjusting device based on a high-speed switching valve according to claim 1, characterized in that A pressure sensor (4) is arranged inside the described convex-shaped roller petal (3).

5. The variable roll diameter tension adjusting device based on a high-speed switching valve according to claim 4, wherein, A slide rail (5) is arranged on the inner side of the described convex-shaped roller petal (3).

6. The variable roll diameter tension adjusting device based on a high-speed switching valve according to claim 1, wherein, Two sets of cylindrical grooves are arranged on the roller shaft (1). One set is located on the left side of the middle plane of the roller shaft (1), and the other set is located on the right side of the middle plane of the roller shaft (1). Each set of cylindrical grooves is evenly distributed circumferentially. The two sets of cylindrical grooves are symmetrically arranged on both sides of the roller shaft (1) and are rotationally offset by 45°. The described radial telescopic hydraulic cylinder (2) is in interference fit with the cylindrical grooves.

7. The variable roll diameter tension adjusting device based on a high-speed switching valve according to claim 6, characterized in that The described radial telescopic hydraulic cylinder (2) includes a push rod (20), a first sealing ring (21), an end cover (22), an outer cylinder body (23), a second sealing ring (24), a piston (25), a displacement sensor (26), a nut (27), and a high-speed switching valve (28). The top of the push rod (20) is threadedly connected to the piston (25), and the tail of the push rod (20) is fixed to the convex-shaped roller petal (3). The piston (25) is located in the cavity of the outer cylinder body (23). A second sealing ring (24) is arranged circumferentially on the piston (25). The nut (27) is fixed to the top of the push rod (20). The displacement sensor (26) is embedded in the top of the push rod (20). The high-speed switching valve (28) is embedded in the outer cylinder body (23) and is symmetrically arranged at the center. The end cover (22) is fixedly connected to the outer cylinder body (23), and a first sealing ring (21) is arranged on the end cover (22).

8. The variable roll diameter tension adjusting device based on a high-speed switching valve according to claim 7, wherein, The described high-speed switching valve (28) includes a housing (2801), a first electromagnetic coil (2802), a first spring (2803), a convex block (2804), a valve core push rod (2805), a sealing ring (2806), a valve body (2807), a first oil hole (2808), a ball core (2809), a filter screen (2810), a plug block (2811), a second spring (2812), a sealing cover (2813), a second oil hole (2814), and a guiding block (2815). The first electromagnetic coil (2802) is fixed inside the housing (2801). The upper end of the convex block (2804) is limit-mounted with the housing (2801) through the first spring (2803). The lower end of the convex block (

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