A double-roller axial variable tension roller centering adjustment mechanism

Abstract

The double-roller axial variable tension roller centering adjusting mechanism fixes the fixed axial variable tension roller in the insert block, and connects the movable axial variable tension roller with the outer support column, and drives the inner support frame to move by cooperation of the second motor, the second worm and gear mechanism, the driving gear and the slider-rack structure, so that the problem of complicated structure and large space occupation of the double-roller axial variable tension roller structure guided by the rack window is avoided; meanwhile, the rotation center of the fixed axial variable tension roller and the rotation center of the movable axial variable tension roller are installed in the same plane, the upper and lower nut seats are driven to move oppositely by cooperation of the first motor, the first worm and gear mechanism and the connecting rod driving lead screw, the synchronous movement of the small connecting rods arranged symmetrically is changed, the position of the guide roller swing rod is driven to change, so that the position of the guide roller is changed, the bisector line of the two rollers is ensured to be located on the symmetric center line of the strip wrapping angle, and the nonlinear problem of the tension stress control is avoided.

Description

Technical Field

[0001] This invention belongs to the field of thin strip rolling technology, and particularly relates to a double-roll axial variable tension roll centering adjustment mechanism. Background Technology

[0002] In the thin strip rolling process, the control of tensile stress directly affects the strip shape quality and dimensional accuracy. According to Saint-Venant's principle, the application of non-uniform tensile stress must be close to the roll gap of the rolling mill to reduce the attenuation and homogenization effect during stress transmission. Therefore, the transverse variable tension roll mechanism must meet the core design requirements of compact structure and close arrangement to the roll gap.

[0003] Existing transverse tension rollers mostly employ a tension control structure with upper and lower double rollers. The strip wraps around the lower tension roller to form a fixed wrap angle, and radial support force is applied through the cooperation of the upper and lower rollers to achieve strip tension adjustment. However, this has significant technical defects: First, double-roller axial tension rollers generally use an external window frame frame with roller system balancing and pressure adjustment devices, resulting in a large overall size. This makes it impossible to achieve a compact arrangement close to the roll gap, violating the stress transfer requirements of the Saint-Venant principle, leading to the failure of uneven tension stress and a significant reduction in strip shape control accuracy. Second, the center line connecting the upper and lower support rollers is difficult to accurately position at the center line of the strip wrap angle, which easily leads to problems such as roller force skew and eccentric arrangement, causing nonlinearity in the pressure control of the roll body.

[0004] Therefore, it is necessary to develop a compact, reliable, and controllable twin-roll axial variable tension roll centering adjustment mechanism that can be integrated with existing rolling mills. Summary of the Invention

[0005] To address the shortcomings and deficiencies of existing technologies, a dual-roller axial variable tension roller centering adjustment mechanism is provided. This mechanism can solve the problems of large structure of existing dual-roller axial variable tension rollers constrained by window frames, which cannot be arranged close to the roll gap, and the nonlinear control of the pressure of the upper and lower tension roller bladders in existing integrated methods after the strip wrap angle changes.

[0006] To achieve the purpose of this invention, a double-roll axial variable tension roll centering adjustment mechanism is provided. The adjustment mechanism includes a fixed axial variable tension roll horizontally arranged inside the mill stand of a rolling mill, with its upper surface flush with the roll gap elevation of the mill. A movable axial variable tension roll is arranged above the fixed axial variable tension roll. Both ends of the movable axial variable tension roll are movably fixed to the free ends of an inner support frame. A guide roll is arranged in front of the movable axial variable tension roll, with both ends movably fixed to the free ends of corresponding guide roll swing arms. The fixed ends of the guide roll swing arms and the fixed ends of the mill stand swing arms are hinged together to an upper nut seat. The free ends of the mill stand swing arms are hinged to... Inside the mill stand archway, the middle of the guide roller swing rod and the stand swing rod are movably fixed to one end of the small connecting rod. The other ends of the two small connecting rods are sleeved together on the lower nut seat. The center of the upper nut seat and the lower nut seat are engaged with two sections of threads with opposite directions on the outer surface of the connecting rod drive screw. The two connecting rod drive screws are respectively inserted into the two side legs of the inner support frame, and the two side legs of the support frame are provided with oppositely arranged slide grooves. The top of the connecting rod drive screw is fixed to the worm gear in the first worm gear mechanism. The rotation shaft of the worm in the first worm gear mechanism is connected to the power output shaft of the first motor. The first worm gear mechanism and the first motor are both fixed on the adjustment platform.

[0007] As a further improvement to the above solution, connecting rods are fixedly installed on both outer sides of the inner support frame. A slider-rack structure is fixed to the free end of the connecting rod. The slider-rack structure is embedded in the convex groove of the outer support column. The rack in the slider-rack structure meshes with the drive gear set in the convex groove. The drive gear is sleeved on the rotating shaft of the worm in the second worm gear mechanism. The worm in the second worm gear mechanism is fixed on the power output shaft of the second motor. The second worm gear mechanism and the second motor are both fixed to the outer side of the outer support column. A rotary shaft is set on the inner side of the lower end of the outer support column. The rotary shaft is inserted into the outer side of the mill stand, and the rotation center of the rotary shaft is coaxial with the rotation center of the fixed axial variable tension roll.

[0008] As a further improvement to the above scheme, an insert is provided between the rolling mill roll system and the rolling mill stand, the end of the fixed axial variable tension roll and the free end of the stand swing arm are inserted into the inner side of the insert, and the end of the rotating shaft is inserted into the outer side of the insert.

[0009] As a further improvement to the above scheme, bearings are provided at the relative rotational positions of the fixed axial tension roller and the insert, and the movable axial tension roller and the free end of the inner support frame.

[0010] As a further improvement to the above scheme, the turbine in the first worm gear mechanism is connected to the top of the connecting rod drive screw by a key.

[0011] The beneficial effects of this invention are:

[0012] Compared with the prior art, the present invention provides a double-roller axial tension variable roller centering adjustment mechanism, which fixes the fixed axial tension variable roller in the insert, and connects the movable axial tension variable roller to the outer support column that rotates coaxially with the fixed axial tension variable roller. The movable axial tension variable roller is moved by the inner support frame driven by the cooperation of a second motor, a second worm gear mechanism, a drive gear, and a slider-rack structure. This adapts to the requirements of the roll gap between the fixed and movable axial tension variable rollers and the self-weight balance of the movable axial tension variable roller, avoiding the need for frame window guidance in double-roller axial tension variable rollers. The tension roller suffers from a complex structure and large space occupation. Meanwhile, the rotation centers of the fixed axial tension roller and the movable axial tension roller are mounted on the same plane. Through the cooperation of a first motor, a first worm gear mechanism, and a connecting rod drive screw, the upper and lower nut seats move in opposite directions, thereby changing the synchronous movement of the symmetrically arranged small connecting rods. This drives the guide roller swing arm to change the position of the guide roller, ensuring that the center line connecting the fixed and movable axial tension rollers is always located on the symmetrical center line of the strip wrap angle, avoiding nonlinearity issues in tension stress control. Attached Figure Description

[0013] Figure 1 This is a schematic diagram showing the relationship between the tensile stress of the strip and the radial support pressure of the tension roll;

[0014] Figure 2 for Force analysis diagram of a twin-roll axial variable tension roll when it coincides with the centerline kk of the strip wrap angle;

[0015] Figure 3 for Force analysis diagram of a double-roller axial variable tension roller when the centerline kk of the strip wrap angle does not coincide with the centerline kk of the strip wrap angle;

[0016] Figure 4 Force analysis diagram of a double-roller axial tension variable tension roller when rotating around the bottom hinge point C to change the strip wrap angle;

[0017] Figure 5 This is an isometric schematic diagram showing the positional relationship between the adjusting mechanism and the rolling mill in this invention;

[0018] Figure 6 This is a side view showing the positional relationship between the adjusting mechanism and the rolling mill in this invention;

[0019] Figure 7 This is a schematic diagram of the first axis of the adjusting mechanism in this invention;

[0020] Figure 8 This is a schematic diagram of the second axis of the adjusting mechanism in this invention;

[0021] Figure 9 This is a side view of the adjusting mechanism in this invention;

[0022] Figure 10 This is a top view of the adjusting mechanism in this invention;

[0023] Figure 11 This is a front view of the adjusting mechanism in this invention;

[0024] Figure 12 for Figure 9 Sectional view AA in the middle;

[0025] Figure 13 for Figure 9 Sectional view BB in the middle;

[0026] Figure 14 for Figure 10 Sectional view CC in the middle;

[0027] Figure 15 for Figure 11 DD in the section view;

[0028] Figure 16 This is a schematic diagram illustrating the working principle of the adjustment mechanism in this invention.

[0029] In the diagram: 1-rolling mill, 2-rolling mill frame archway, 3-fixed axial tension variable roll, 4-movable axial tension variable roll, 5-inner support frame, 6-guide roll, 7-guide roll swing arm, 8-frame swing arm, 9-upper nut seat, 10-small connecting rod, 11-lower nut seat, 12-connecting rod drive screw, 13-first worm gear mechanism, 14-first motor, 15-adjustment platform, 16-connecting rod, 17-slider-rack structure, 18-outer support column, 19-convex groove, 20-drive gear, 21-second worm gear mechanism, 22-second motor, 23-rotating shaft, 24-rolling mill roll system, 25-insert, 26-lower roll of double-roll axial tension variable roll, 27-upper roll of double-roll axial tension variable roll, 28-strip. Detailed Implementation

[0030] The specific embodiments of the present invention will be further described in detail below with reference to the accompanying drawings:

[0031] The structural principle of axial variable tension rollers for zoned tension stress: Figure 1 This relates to the relationship between the tensile stress of the strip and the radial support pressure of the tension roll. When the tension roll is working, the strip wraps around it at a certain angle, and the segmented capsules of the tension roll act on the strip to create zoned radial support reaction forces. The tensile stress at the end of the strip covered by the tension roller The combined force formed A balance is formed.

[0032] When the wrap angle equals At that time, the pressure within any segment of the inflatable bladder is Acting on local width The radial support reaction force is:

[0033] ,

[0034] Local width at both ends of the strip Tensile stress The combined force formed equal

[0035] ,

[0036] radial support reaction force of tension roller bladder Tensile stress at both ends of the strip The combined force Achieving equilibrium of spatial force systems:

[0037] ,

[0038] This allows us to obtain the pressure required within the expandable bladder of the tension roller. The tensile stress that needs to be compensated locally in the strip The relationship is:

[0039] ,

[0040] In the above formula, h is the thickness of the strip; It is the wrap angle of the strip on the tension roller. This refers to the local width of the strip. The nominal radius of the tension roller. This refers to the localized tensile stress at the end of the strip. This refers to the internal pressure of the cyst.

[0041] When the two rollers are in operation, the strip passes through the middle of the two rollers, with the lower roller having a very small width. Support force of the region on the strip The upper roller has a very small width. Pressure acting on the strip in the region ,like Figures 2-4 As shown, its tension at both ends of the strip , Forming a system of balanced forces Figures 2-4 In the diagram, number 26 refers to the lower roll of a twin-roll axial variable tension roll, number 27 refers to the upper roll of a twin-roll axial variable tension roll, and number 28 refers to the strip. When the centerline of the upper and lower rolls... When it coincides with the symmetrical centerline kk of the strip wrap angle, that is... Figure 2 The state shown indicates a force balance relationship in the x and y directions:

[0042] ,

[0043] According to the equilibrium relationship, we can obtain...

[0044] ,

[0045] According to the force balance relationship, we can obtain...

[0046] ,

[0047] ,

[0048] For a lower roller with a certain wrap angle, the concentrated force

[0049] ,

[0050] For the upper roller, it is approximately a concentrated force.

[0051] ,

[0052] Therefore, we can obtain

[0053] ,

[0054] When the center line of the upper and lower rollers The deviation from the symmetrical centerline of the strip wrap angle kk reaches At an angle, that is Figure 3 The state shown indicates a force balance relationship in the x and y directions.

[0055] ,

[0056] Based on the foregoing analysis and stress balance relationship, we can obtain...

[0057] ,

[0058] ,

[0059] when As shown in the above formula, the tensile stress on both sides of the transverse variable tension roll is not equal, and the larger the angle, the greater the difference in tensile stress, resulting in one side of the strip being tight and the other loose. When the tensile stress is asymmetrically distributed along the roll body axis, it easily causes the strip to deviate, leading to waviness in the deformation zone. Furthermore, the supporting force of the upper and lower sections of the double-roll axial variable tension roll... , and the tensile stress before and after strip , The relationship is nonlinear, meaning that when the line connecting the axes of the upper and lower tension rollers is not on the symmetrical center line of the lower roller's wrap angle, it will inevitably bring difficulties to the control of each bladder of the upper and lower tension rollers.

[0060] When a twin-roll axial tension variable tension roller, such as the tension roller wrap angle adjustment method mentioned in patent CN202510473627.7, rotates around the bottom hinge point C to change the strip wrap angle, it is similar to... Figure 4 In the state shown, since the positions of the inlet or outlet point A of the deformation zone and the guide roller point B remain unchanged, rotation around the hinge point C in the diagram will cause a change in the wrap angle between the strip and the upper and lower tension rollers. The centerlines of the upper and lower roller systems will no longer be effectively distributed on the symmetrical centerline of the strip's wrap angle. At this time, the effect of the upper roller on the strip is similar to... Figure 3 As shown, the tension roller is not distributed on the center line of the strip wrap angle, which will significantly cause stress difference before and after the tension roller, and cause nonlinear relationship of the pressure of the segmented bladder of the upper and lower rollers, affecting the control of the bladder fluid pressure.

[0061] To address the issues of large size of existing window-frame-constrained twin-roll axial variable tension roll structures, which cannot be arranged close to the roll gap, and the nonlinear control of the upper and lower tension roll pressure in existing integrated methods after the strip wrap angle changes, such as... Figures 5-15 As shown, this invention provides a double-roll axial variable tension roll centering adjustment mechanism. A fixed axial variable tension roll 3 is horizontally arranged inside the mill stand 2 of the mill 1, with its upper surface flush with the roll gap elevation of the mill 1. A movable axial variable tension roll 4 is arranged above the fixed axial variable tension roll 3. Both ends of the movable axial variable tension roll 4 are movably fixed to the free ends of the inner support frame 5. A guide roll 6 is arranged in front of the movable axial variable tension roll 4, with both ends movably fixed to the free ends of corresponding guide roll swing rods 7. The fixed ends of the guide roll swing rods 7 and the fixed ends of the mill stand swing rods 8 are hinged together to the upper nut seat 9. The free ends of the mill stand swing rods 8 are hinged to the inner side of the mill stand 2. The middle parts of the roller swing arm 7 and the frame swing arm 8 are movably fixed to one end of the small connecting rod 10. The other ends of the two small connecting rods 10 are sleeved together on the lower nut seat 11. The center of the upper nut seat 9 and the lower nut seat 11 are engaged with two sections of threads with opposite directions on the outer surface of the connecting rod drive screw 12. The two connecting rod drive screws 12 are respectively inserted into the two side legs of the inner support frame 5, and the two side legs of the support frame 5 are provided with oppositely arranged slide grooves. The top of the connecting rod drive screw 12 is connected to the worm gear in the first worm gear mechanism 13 by a key. The rotation shaft of the worm in the first worm gear mechanism 13 is connected to the power output shaft of the first motor 14. The first worm gear mechanism 13 and the first motor 14 are both fixed on the adjustment platform 15.

[0062] During operation, the first motor 14 drives the worm in the first worm gear mechanism 13 to rotate, thereby using the worm and worm gear to drive the connecting rods on both sides to rotate. The connecting rods drive the lead screw 12 with two threads of opposite direction on the outer surface, which respectively drive the upper nut seat 9 and the lower nut seat 11 to move in opposite directions and away from each other. Under the traction of the fixed end of the frame swing rod 8, the tilt angle of the inner support frame 5 is changed. At the same time, the guide roller swing rod 7 changes the position of the guide roller 6, changes the strip wrap angle, and ensures that the plane containing the axes of the movable axial tension roller 4 and the fixed axial tension roller 3 is always located on the symmetrical center line of the strip wrap angle.

[0063] Meanwhile, connecting rods 16 are fixedly installed on both outer sides of the inner support frame 5. A slider-rack structure 17 is fixed to the free end of the connecting rod 16. The slider-rack structure 17 is embedded in the convex groove 19 of the outer support column 18. The rack in the slider-rack structure 17 meshes with the drive gear 20 set in the convex groove 19. The drive gear 20 is sleeved on the rotating shaft of the worm in the second worm gear mechanism 21. The worm in the second worm gear mechanism 21 is fixed on the power output shaft of the second motor 22. The second worm gear mechanism 21 and the second motor 22 are both fixed to the outer side of the outer support column 18. A rotating shaft 23 is set on the inner side of the lower end of the outer support column 18. The rotating shaft 23 is inserted into the outer side of the mill stand 2 and the rotation center of the rotating shaft 23 is coaxial with the rotation center of the fixed axial variable tension roll 3.

[0064] During operation, the second motor 22 drives the turbine of the second worm gear mechanism 21 to rotate, thereby using the worm and turbine to drive the drive gear 20 to rotate. The drive gear 20 meshes with the rack in the slider-rack structure 17, thereby driving the slider in the slider-rack structure 17 to move up and down along the convex groove 19. Then, the connecting rod 16 fixed to the slider in the slider-rack structure 17 drives the inner support frame 5 to move up and down. The movable axial tension roller 4 fixed to the inner support frame 5 naturally moves up and down as well. This changes the roll gap between the movable axial tension roller 4 and the fixed axial tension roller 3, the pre-pressure of the movable axial tension roller 4 on the upper surface of the strip, and the tension control for rolling strips of different thicknesses.

[0065] Since the worm gear can achieve self-locking and the motor has a braking function, when the first motor 14 or the second motor 22 is stationary, the movable axial tension roller 4 is fixed in position and does not slide through the self-locking between the first motor 14 and the first worm gear mechanism 13 or between the second motor 22 and the second worm gear mechanism 21.

[0066] In addition, an insert 25 is provided between the mill roll system 24 of the mill 1 and the mill stand 2. The end of the fixed axial tension variable roll 3 and the free end of the stand rocker arm 8 are inserted into the inner side of the insert 25, and the end of the rotating shaft 23 is inserted into the outer side of the insert 25. Bearings are provided at the relative rotation positions of the fixed axial tension variable roll 3 and the insert 25, and the movable axial tension variable roll 4 and the free end of the inner support frame 5.

[0067] This invention provides a double-roller axial variable tension roller centering adjustment mechanism, the working principle of which is as follows: Figure 16 As shown, the axis ST connecting the fixed axial variable tension roller 3 and the movable axial variable tension roller 4 always coincides with the rod QD of the connecting rod drive screw 12. The rod QD has two sections of threads with different helical directions, which drive the movement of point E of the upper nut seat 9 and point F of the lower nut seat 11, respectively. The rod FJ of the frame swing arm 8 is hinged to the insert 25 of the mill 1 through point J, approximately hinged at the mill roll gap position. The length of the rod FJ of the frame swing arm 8 is equal to the length of the rod FI of the guide roller swing arm 7. The rods EG and EH of the symmetrically arranged small connecting rods 10 are equal in length. The rod Q of the connecting rod drive screw 12... Rotation D causes point E of the upper nut seat 9 and point F of the lower nut seat 11 to move in opposite directions or in the opposite direction. This causes the angle ∠IFJ between the rod FJ of the frame swing arm 8 and the rod FI of the guide roller swing arm 7 to change, while ensuring that the angles ∠EFG and ∠EFH are always the same. Under the connection of the rod FJ of the frame swing arm 8, the rod QD of the connecting rod drive screw 12 drives the movable axial tension roller 4 to rotate around the rotation center T of the fixed axial tension roller 3, and it is always located on the symmetrical center line of ∠IFJ, thus ensuring that the connecting line ST is always located on the symmetrical center line of the wrap angle of the strip LK.

[0068] During the rotation process, the strip wrap angle formed by the guide roller 6, the upper roller surface of the fixed axial tension roller 3, and the mill roll gap changes due to the position change of the guide roller 6, but always keeps the plane of the rotation center line of the movable axial tension roller 4 and the fixed axial tension roller 3 on the center line of the strip wrap angle, thus avoiding the nonlinear problem of strip tension stress control.

[0069] The above embodiments are not limited to the technical solutions of the embodiments themselves, and the embodiments can be combined with each other to form new embodiments. The above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit them. Any modifications or equivalent substitutions that do not depart from the spirit and scope of the present invention should be covered within the scope of the technical solutions of the present invention.

Claims

1. A double-roller axial variable tension roller centering adjustment mechanism, characterized in that: The adjusting mechanism has a fixed axial tension roller (3) horizontally arranged inside the mill frame archway (2) of the mill (1), and the upper surface of the fixed axial tension roller (3) is flush with the roll gap elevation of the mill (1). A movable axial tension roller (4) is arranged above the fixed axial tension roller (3). The two ends of the movable axial tension roller (4) are movably fixed to the free ends of the inner support frame (5). A guide roller (6) is arranged on the front side of the movable axial tension roller (4). The two ends of the guide roller (6) are movably fixed to the free ends of the corresponding guide roller swing rod (7). The fixed end of the guide roller swing rod (7) and the fixed end of the frame swing rod (8) are hinged together with the upper nut seat (9). The free end of the frame swing rod (8) is hinged to the inside of the mill frame archway (2). The guide roller swing rod (7), the frame swing rod (8 ... The middle part of the swing arm (8) is movably fixed to one end of the small connecting rod (10). The other ends of the two small connecting rods (10) are sleeved together on the lower nut seat (11). The center of the upper nut seat (9) and the lower nut seat (11) are engaged with two sections of oppositely helical threads on the outer surface of the connecting rod drive screw (12). The two connecting rod drive screws (12) are respectively inserted into the two side legs of the inner support frame (5), and the two side legs of the support frame (5) are provided with relatively arranged slide grooves. The top of the connecting rod drive screw (12) is fixed to the worm in the first worm gear mechanism (13). The rotation shaft of the worm in the first worm gear mechanism (13) is connected to the power output shaft of the first motor (14). The first worm gear mechanism (13) and the first motor (14) are both fixed on the adjustment platform (15).

2. The double-roller axial variable tension roller centering adjustment mechanism according to claim 1, characterized in that: Connecting rods (16) are fixedly installed on both outer sides of the inner support frame (5). A slider-rack structure (17) is fixed to the free end of the connecting rod (16). The slider-rack structure (17) is embedded in the convex groove (19) of the outer support column (18). The rack in the slider-rack structure (17) meshes with the drive gear (20) provided in the convex groove (19). The drive gear (20) is sleeved on the worm in the second worm gear mechanism (21). On the rotating shaft, the turbine in the second worm gear mechanism (21) is fixed on the power output shaft of the second motor (22). The second worm gear mechanism (21) and the second motor (22) are both fixed on the outside of the outer support column (18). A rotating shaft (23) is provided on the inner side of the lower end of the outer support column (18). The rotating shaft (23) is inserted into the outside of the mill frame archway (2) and the rotation center of the rotating shaft (23) is coaxial with the rotation center of the fixed axial variable tension roll (3).

3. The double-roller axial variable tension roller centering adjustment mechanism according to claim 2, characterized in that: An insert (25) is provided between the mill roll system (24) of the mill (1) and the mill frame archway (2). The end of the fixed axial variable tension roll (3) and the free end of the frame swing rod (8) are inserted into the inner side of the insert (25), and the end of the rotating shaft (23) is inserted into the outer side of the insert (25).

4. The double-roller axial variable tension roller centering adjustment mechanism according to claim 3, characterized in that: Bearings are provided at the relative rotational positions of the fixed axial tension roller (3) and the insert (25), and the movable axial tension roller (4) and the inner support frame (5).

5. The double-roller axial variable tension roller centering adjustment mechanism according to claim 4, characterized in that: The turbine in the first worm gear mechanism (13) is connected to the top of the connecting rod drive screw (12) by a key.

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