Roll changing mechanism with clearance compensation function

Abstract

The roller changing mechanism with the clearance compensation function comprises a rack used for being placed at the upper end of a bearing seat, the lower end of the rack is slidably connected with two carrier roller seats in bilateral symmetry in the left-right direction, each carrier roller seat comprises two supporting parts opposite in the front-back direction, and an avoiding groove with the open lower end and capable of avoiding a roller shaft is formed between the two supporting parts; bearing parts are arranged on the inner sides of the supporting parts, the two bearing parts which are opposite front and back form a carrier roller assembly used for bearing a roller body of the lower brush roller, clearance compensation assemblies are arranged on the left side and the right side of the rack correspondingly, and each clearance compensation assembly comprises a lifting part capable of moving in the longitudinal direction; the clearance compensation assemblies are arranged on the left side and the right side of the machine frame, the lifting piece capable of moving in the longitudinal direction moves downwards to abut against the bearing base to lift the machine frame upwards by the preset height, the bearing piece is attached to the roller body while the preset clearance is eliminated, the situation that a roller shaft of the lower brush roller deforms when being disengaged from the roller base is avoided, and the service life of the lower brush roller is prolonged. The service life of the lower brush roller is prolonged; and the roller replacement efficiency is improved.

Description

Technical Field

[0001] The invention relates to the field of plate and strip grinding, and in particular to a roller changing mechanism with a gap compensation function. Background Art

[0002] After the steel plate is produced, it will be rolled up and stored, that is, steel coils. The steel coils will then enter the processing plant and be made into parts. During the period from the time the plate enters the processing plant to the time the plate is cut and processed, the surface material of the plate is prone to peeling or rusting. In order to remove the rust layer, the plate needs to be polished by the upper and lower brush rollers relative to each other in the steel plate grinding equipment; the upper brush roller and the lower brush roller both include a roller body and roller shafts located at both ends of the roller body; after a long period of grinding, the grinding effect of the brush roller will also decrease, so the brush roller needs to be replaced.

[0003] When replacing the upper brush roller, the roller changing vehicle can be driven into the brush grinding equipment for receiving and replacing, but the lower brush roller can usually only be replaced manually. For example, in the oxide skin treatment device with announcement number CN216371592, two bearing seats are arranged on the bearing seat, one of which is slidable and the other is fixed, which can be respectively regarded as a sliding seat and a fixed seat; the roller shafts at both ends of the lower brush roller are respectively stuck in the sliding seat and the fixed seat; when changing the roller, it is necessary to move the bearing seat out of the equipment, and then rely on workers to use slings to hang the roller body of the lower brush roller, so that the sliding seat and the fixed seat are respectively disengaged from the roller shafts at both ends of the lower brush roller; but the force of the sling is difficult to control, and the lower brush roller is easy to deflect, resulting in deformation of the roller shaft stuck in the bearing seat, high operation difficulty, and low roller changing efficiency.

[0004] The applicant has designed a mechanism for changing rollers from the upper end of a bearing seat, comprising a frame that can be hoisted on the upper end of the bearing seat, two roller seats slidably connected to the frame are provided at the lower end of the frame, the roller seat comprises two front and rear opposing support parts, an escape groove with an open lower end and for evading the roller shaft is provided between the two support parts, a supporting member is provided on the inner side of the support part, and the two front and rear opposing supporting members constitute a roller assembly, when the two roller seats approach each other and the two roller assemblies support the roller body of the lower brush roller, the lower brush roller remains stable, at which time the sliding seat and the fixed seat can respectively disengage the two ends of the lower brush roller and keep the roller shaft of the lower brush roller unchanged.

[0005] However, the difficulty in design lies in that it is difficult for the supporting member to fit closely with the roller body of the lower brush roller. Ideally, when the two roller seats approach each other, each supporting member should be closely attached to the roller body of the lower brush roller. However, in the actual situation, due to the existence of manufacturing and installation errors, there will always be a slight deviation in the installation position of the supporting member, making it difficult to just fit closely with the roller body. If the front-to-back distance between the two supporting members is too close, the supporting member will also collide and interfere with the roller. Therefore, to avoid this phenomenon, the distance between the two front-to-back opposite supporting members needs to be relatively wide, so that after the two roller seats are moved into place, a preset gap is formed between the supporting member and the roller body. However, after leaving the preset gap, the supporting member is separated from the roller body again. When the sliding seat disengages from the roller shaft at one end of the lower brush roller, the roller shaft at the other end of the lower brush roller stuck in the fixed seat will still deform. Summary of the Invention

[0006] The present invention provides a roll-changing mechanism with a gap compensation function. By arranging gap compensation components on the left and right sides of the frame, the liftable member that can move longitudinally moves downward to press against the bearing seat and then lift the frame upward by a predetermined height. While eliminating the preset gap, the supporting member is made to fit closely with the roller body, avoiding deformation when the roller shaft of the lower brush roller disengages from the roller seat, and improving the service life and roll-changing efficiency of the lower brush roller.

[0007] The technical solution of the present invention is realized as follows: A roll-changing mechanism with a gap compensation function includes a frame for placing on the upper end of the bearing seat. Two left-and-right symmetrically arranged roller seats are slidably connected to the lower end of the frame in the left-and-right direction. The roller seat includes two front-to-back opposite supporting parts. There is an avoidance groove with an open lower end and for avoiding the roller shaft between the two supporting parts. A supporting member is arranged inside the supporting part. Two front-to-back opposite supporting members constitute a roller supporting assembly for supporting the roller body of the lower brush roller. Gap compensation components are arranged on both the left and right sides of the frame. The gap compensation component includes a liftable member that can move longitudinally. When the two roller seats slide in the left-and-right direction and drive the two roller supporting assemblies to approach each other to a predetermined position, a preset gap is formed between each supporting member and the roller body. At this time, the liftable member can move downward to act on the bearing seat, thereby lifting the frame and the two roller seats upward by a predetermined height to eliminate the preset gap and make the supporting member fit closely with the roller body.

[0008] Preferably, the gap compensation component includes a driving component and a transmission component. The transmission component includes a transmission wheel arranged on the frame. A connecting rod is arranged between the transmission wheel and the liftable member. The lower end of the connecting rod is hinged to the liftable member, and the upper end of the connecting rod is eccentrically rotationally connected to the transmission wheel. The driving component can drive the transmission wheel to rotate synchronously by a predetermined angle and drive the liftable member to extend downward by a predetermined length to act on the bearing seat, thereby lifting the frame and the two roller seats upward by a predetermined height. The eccentric connection causes the entire connecting rod to generate a displacement longitudinally when the transmission wheel rotates, driving the liftable member to extend downward and act on the bearing seat.

[0009] Preferably, the driving wheel is a driving gear, the driving assembly includes two driving gears facing each other front and back, the number of connecting rods corresponds to the number of driving gears, the driving assembly includes a driving shaft and two driving gears, and a linkage rod is connected between the two driving gears on the left and right sides; the corresponding driving gears are simultaneously meshed with the two driving gears facing each other front and back on the left or right side; the driving shaft directly or indirectly acts on one of the driving gears, and an adjusting handwheel is connected to the outer end of the driving shaft. By rotating the adjusting handwheel, the plurality of driving gears are rotated by a predetermined angle and stopped at corresponding positions.

[0010] Preferably, a self-locking transmission member is provided between the driving shaft and the corresponding driving gear. The self-locking transmission member is a worm and worm gear transmission box. The driving shaft is connected to the input end of the worm and worm gear transmission box, and the corresponding driving gear is connected to the output end of the worm and worm gear transmission box; after the driving gear rotates to the in-place position, the worm and worm gear transmission box restricts the reverse rotation of the driving gear, so that the two driving wheels stop at the predetermined positions; preventing the driving wheels from reversing and keeping the lifting member in the downward extended state.

[0011] Preferably, a central hole is provided in the middle of the driving wheel, a rotating shaft hole is provided at the upper end of the connecting rod, and an eccentric assembly is installed in the rotating shaft hole. The eccentric assembly includes a transmission shaft and an eccentric sleeve. An eccentric hole that is not concentric with the rotating shaft hole is provided on the eccentric sleeve. The transmission shaft passes through the eccentric hole and the central hole and is circumferentially fixed with the eccentric sleeve and the driving wheel; the driving wheel rotates to drive the lifting member to extend downward; while the eccentric sleeve can form an eccentric drive for the connecting rod, it can ensure uniform stress distribution of the driving wheel.

[0012] Preferably, an eccentricity is formed between the center of the eccentric hole and the center of the rotating shaft hole, and the size of the eccentricity is equal to one-half of the predetermined height; and the predetermined angle of synchronous rotation of the plurality of driving wheels is 180 degrees; in the initial state, the center of the rotating shaft hole is directly above the center of the central hole; when the plurality of driving wheels rotate synchronously by 180 degrees, the center of the rotating shaft hole moves to directly below the center of the central hole.

[0013] Preferably, when the synchronous rotation angle of the plurality of driving wheels is greater than 180 degrees, the center of the rotating shaft hole rotates around the center of the central hole and approaches the initial position, and drives the two lifting members that have extended downward to reset upward; preventing excessive rotation from causing excessive lifting of the frame and avoiding deformation of the roller shaft due to an upward acting force on the roller.

[0014] Preferably, the clearance compensation assembly includes two lifting cylinders that are spaced apart front and back and are arranged on the left and right sides of the frame, and the lifting member is a lifting rod that telescopically extends longitudinally in the lifting cylinder.

[0015] Preferably, the clearance compensation assembly includes screws arranged on the left and right sides of the frame, and the lifting member is a lifting inner screw sleeve threadedly connected to the lower end of the screw. A handle is connected to the outer wall of the lifting inner screw sleeve. By rotating the handle, the lifting inner screw sleeve rotates circumferentially and extends downward.

[0016] The beneficial effects of the present invention adopting the above technical solutions are as follows: In the present invention, by arranging gap compensation components on the left and right sides at the lower end of the frame, when a preset gap is formed between the supporting members on the two roller seats and the roller body of the lower brush roller, the lifting member therein moves longitudinally to act on the bearing seat, lifting the frame and the two roller seats upward by a predetermined height, compensating and eliminating the preset gap, ensuring that the supporting member forms just the right rigid support for the roller body; avoiding the deformation of the roller shaft when the lower brush roller disengages from the sliding seat and the fixed seat, and ensuring the use quality and roll changing efficiency of the lower brush roller. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 It is a structural diagram of the roll changing mechanism; Figure 2 It is a schematic structural diagram of the roll changing mechanism from another angle; Figure 3 It is a cross-sectional view of the roller body of the lower brush roller supported by two front and rear opposite supporting members; Figure 4 It is a schematic diagram of the roll changing mechanism placed on the upper end of the bearing seat; Figure 5 It is a schematic diagram of the sliding seat disengaging from one end of the roller shaft of the lower brush roller after the roller body of the lower brush roller is supported; Figure 6 It is a schematic diagram of the pushing cylinder acting and disengaging the roller shaft at the other end of the lower brush roller from the fixed seat; Figure 7 It is a structural diagram of the gap compensation component after hiding the frame; Figure 8 It is a cross-sectional view of the gap compensation component; Figure 9 It is an enlarged cross-sectional view of the matching position between the upper end of the connecting rod and the transmission shaft; Figure 10 It is an enlarged view of the pointer and the dial on the frame; Figure 11 It is a structural diagram of the eccentric sleeve; Figure 12 It is a structural diagram of the positioning and adjusting component; Figure 13 It is a structural diagram of the lower brush roller supported by two roller supports; Figure 14 It is a structural diagram of the roller support; Figure 15 It is a schematic diagram of the principle of roll changing of the roll changing mechanism at the upper end of the bearing seat; Figure 16 It is a cross-sectional comparison diagram when the preset gap exists and when the preset gap is eliminated; Figure 17 It is a schematic diagram of the gap compensation component in Embodiment 2; Figure 18 It is a schematic diagram of the clearance compensation component in Embodiment 3; Each reference numeral is as follows: 1 - frame, 1a - bearing seat, 2 - idler roller seat, 3 - pushing oil cylinder, 4 - clearance compensation component, 5 - roller body, 6 - lifting oil cylinder, 7 - screw, 11 - first lifting lug, 12 - second lifting lug, 13 - first lifting hole, 13a - second lifting hole, 14 - sliding seat, 15 - fixed seat, 16 - guiding seat, 17 - guiding wheel, 18 - hydraulic station, 21 - linkage oil cylinder, 22 - supporting member, 23 - control handwheel, 24 - supporting part, 25 - cross plate, 26 - mounting plate, 27 - reinforcing plate, 41 - driving shaft, 42 - worm and worm gear transmission box, 43 - transmission component, 51 - circular boss, 71 - screw, 72 - lifting internal screw sleeve, 221 - supporting surface, 222 - limiting surface, 231 - adjusting rack, 232 - adjusting gear, 241 - avoiding groove, 242 - abutting surface, 251 - connecting seat, 252 - rotating shaft sleeve, 261 - fixing plate, 411 - adjusting handwheel, 412 - pointer, 413 - scale disk, 431 - driving gear, 432 - transmission wheel, 432a - transmission shaft, 433 - connecting rod, 434 - lifting plate, 435 - guiding plate, 436 - eccentric sleeve, 4361 - eccentric hole, 4362 - retaining ring groove, 4363 - annular groove, 437 - spherical plain bearing, 438 - output shaft, 439 - linkage rod, s - preset clearance. Detailed implementation manners

[0018] In order to more clearly understand the above objects, features and advantages of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific implementation manners. It should be noted that, without conflict, the embodiments of the present application and the features in the embodiments can be combined with each other.

[0019] In the following description, many specific details are set forth in order to fully understand the present invention. However, the present invention can also be implemented in other ways different from those described herein. Therefore, the protection scope of the present invention is not limited by the specific embodiments disclosed below.

[0020] The present invention has multiple implementation manners, and the specific implementation manners are as follows: Embodiment 1: As Figure 1-16 shown, this embodiment provides a roll changing mechanism with a clearance compensation function. This roll changing mechanism is used for changing rolls on the bearing assembly that clamps the lower brush roll. The bearing assembly includes a bearing seat 1a, a sliding seat 14 and a fixed seat 15 that are arranged on the bearing seat 1a and are used for clamping the two ends of the roller shaft of the lower brush roll. The sliding seat 14 can slide along the length direction of the lower brush roll; the sliding seat 14 and the fixed seat 15 are arranged in a box body with a single - side opening on the bearing seat 1a; In this embodiment, the roll-changing mechanism with a clearance compensation function includes a frame 1 placed on the upper end of a bearing seat 1a, and the frame 1 is placed on the upper end of a box body; two symmetrically arranged roller seats 2 are slidably connected to the lower end of the frame 1 in the left-right direction. The roller seat 2 includes two support parts 24 opposite to each other in the front-back direction. There is a clearance groove 241 with an open lower end and avoiding the roller shaft between the two support parts 24. A supporting member 22 is provided inside the support part 24. Two supporting members 22 opposite to each other in the front-back direction form a roller assembly for supporting the roller body 5 of the lower brush roller. Clearance compensation components are provided on both the left and right sides of the frame 1. The clearance compensation component includes a lifting member that can move longitudinally; When the two roller seats 2 slide in the left-right direction and drive the two roller assemblies to approach each other to a predetermined position, a preset clearance s is formed between each supporting member 22 and the roller body 5. At this time, the lifting member can move downward to act on the bearing seat 1a, so as to lift the frame 1 and the two roller seats 2 upward by a predetermined height to eliminate the preset clearance s and make the supporting member 22 in close contact with the roller body 5.

[0021] Furthermore, a telescopic linkage member for driving the two roller seats 2 to approach each other is provided between the two roller seats 2; a telescopic pushing member is provided on the roller seat 2 facing the fixed seat 15; the roller seat 2 includes two support parts 24 opposite to each other in the front-back direction and extending downward. A supporting member 22 is connected inside the support part 24; a clearance area 241 with an open lower end is formed between the two support parts 24; the two clearance areas 241 correspond to the positions of the roller shafts at both ends of the lower brush roller respectively; In the working state, the telescopic linkage member drives the two roller seats 2 to approach each other, and makes two groups of supporting members 22 opposite to each other in the front-back direction move to a predetermined position to form a rigid support for the roller body 5 of the lower brush roller. When the sliding seat 14 disengages from the roller shaft at one end of the lower brush roller, the telescopic pushing member expands and contracts and acts on the fixed seat 15, so that the two roller seats 2 slide in the direction away from the fixed seat 15, so that the roller shaft at the other end of the lower brush roller disengages from the fixed seat 15.

[0022] Furthermore, the roller body 5 of the lower brush roller includes a roller barrel for arranging brush strips. The outer diameter of the roller barrel is much larger than the outer diameter of the roller shaft. If the brush strips are not considered, the supporting member 22 can support on the roller barrel. However, to avoid the supporting member 22 contacting the brush strips on the roller barrel and causing the brush strips to deform, circular bosses 51 for arranging roller shafts are concentrically installed at both the left and right ends of the roller barrel. The outer diameter of the circular boss 51 is smaller than the outer diameter of the roller barrel; after the two roller seats 2 approach each other to a predetermined position, the fact that the supporting member 22 forms a support for the roller body 5 in this embodiment means that after the supporting member 22 moves into place along with the roller seat 2, it forms a support for the outer periphery of the circular boss 51, ensuring that the brush strips of the lower brush roller are not deformed by the extrusion of the supporting member 22.

[0023] Furthermore, in order to place the roll-changing mechanism on the upper end of the bearing seat 1a, a hoisting method is adopted in this embodiment. The sling needs to be first hung on the hook of the overhead crane, and then the two ends of the sling are respectively hung on the frame 1. To ensure that the hoisted roll-changing mechanism remains horizontal, a hoisting leveling assembly is provided on the frame 1. The hoisting leveling assembly includes a first lifting lug 11 and a second lifting lug 12 that are horizontally opposite to each other. A single first lifting hole 13 is provided on the first lifting lug 11, and a plurality of horizontally spaced second lifting holes 13a are provided on the second lifting lug 12. One end of the flexible sling is hoisted in the first lifting hole 13, and the other end of the flexible sling is hoisted on one of the plurality of second lifting holes 13a. That is to say, the operator can switch the hanging end of the sling among the plurality of second lifting holes 13 until the first lifting lug 11 and the second lifting lug 12 are at the same height position, so that the hoisted roll-changing mechanism remains horizontal.

[0024] Furthermore, to ensure that when the roll-changing mechanism is placed in place on the upper end of the bearing seat 1a, a front-back guiding mechanism and a left-right guiding mechanism are provided between the frame 1 and the bearing seat 1a. The front-back guiding mechanism includes an elastic guiding wheel 17 provided on the frame 1 and a guiding block provided on the bearing seat 1a. The left-right guiding mechanism includes a guiding seat 16 provided on the frame 1 and a guiding column provided on the bearing seat 1a. Through the cooperation of the elastic guiding wheel 17 and the guiding block, and the cooperation of the guiding seat 16 and the guiding column, the position of the roll-changing mechanism in the hoisting state can be guided, so that it is stably placed at the corresponding position on the upper end of the bearing seat 1a. The specific structures of the front-back guiding mechanism and the left-right guiding mechanism can refer to the corresponding content in the idler device patent with the publication number CN221821042, which will not be elaborated here.

[0025] Furthermore, the structure of the idler seat 2 is as follows: The idler seat 2 includes a horizontal plate 25 for slidably connecting to the frame 1. A support is connected to the lower end of the horizontal plate 25. A middle position at the lower end of the support is concavely formed with two front-back opposite support portions 24 and an avoidance groove 241 between the two support portions 24. A longitudinal plate 26 is provided between the horizontal plate 25 and each support portion 24. The longitudinal plate 26 is both the carrier for installing the linkage oil cylinder 21 and plays a strengthening role between the cross plate 25 and the support portion 24. The aforementioned telescopic linkage is connected between every two left-right opposite longitudinal plates 26, enabling the front and rear ends of the idler seat 2 to move synchronously. There are two connecting ears at the head end position of the piston rod and the tail end position of the cylinder body, and the width between the two connecting ears is greater than the thickness of the longitudinal plate 26. To ensure the hinge is in place, a fixing plate 261 is connected to the longitudinal plate 26, and hinge holes are simultaneously machined on the longitudinal plate 26 and the fixing plate 261. The fixing plate 261 can increase the thickness of the longitudinal plate 26 to make up for the gap between the longitudinal plate 26 and the connecting ear, so that after the linkage oil cylinder 21 is hinged in place, the linkage oil cylinder 21 remains stable in the front-back direction.

[0026] Furthermore, to ensure the structural strength of the idler bracket 2, the idler bracket 2 is a welded structural member. A support is provided at the lower end of the horizontal plate 25, and the middle position at the lower end of the support is recessed inward, thereby forming two support portions 24 and a relief groove 241 located between the two support portions 24. To ensure the light weight of the idler bracket 2, the support is a hollow structure, including at least two vertical plates 243 spaced left and right and welded to the lower end of the horizontal plate 25. The middle parts of the lower ends of the two vertical plates 243 are recessed inward, thereby forming two support portions 24 and a relief groove 241 located between the two support portions 24. A connecting plate 244 is fixedly installed between every two adjacent vertical plates 243, and the connecting plate 244 and the two vertical plates 243 form the hollow support.

[0027] Furthermore, as Figure 13-14 shown, to ensure the stability of the lower brush roller when it disengages from the sliding seat 14 and the fixed seat 15, an outwardly open support groove is provided on the support member 22. The support groove includes a support surface 221 for supporting the lower brush roller and a vertical limiting surface 222 perpendicular to the support surface 221. To further conform to the circular boss 51 of the roller body 5, the support surface 221 is an arc surface. When the two idler assemblies support the lower brush roller, the vertical limiting surfaces 222 on the left and right sides respectively abut against the two end faces of the lower brush roller to prevent the lower brush roller from moving left and right when it disengages from the sliding seat 14 and the fixed seat 15. Here, the two end faces of the lower brush roller refer to the outer end faces of the two circular bosses 51. When the two limiting surfaces 222 are respectively in contact with the outer end faces of the two circular bosses 51, the support member 22 can effectively prevent the lower brush roller from moving horizontally.

[0028] Furthermore, the area of the limiting surface 222 on the support member 22 is small, and there are only two support members 22 on each idler bracket 2. The two limiting surfaces 222 of the two support members 22 can only form two limiting points on the outer end face of the roller body 5. Therefore, to increase the stability of the roller body 5, a abutting plate for contacting the end face of the roller body of the lower brush roller is provided on the inner side of the support portion 24. A abutting surface 242 is provided on the abutting plate, and the abutting surface 242 and the limiting surface 222 are in the same vertical plane to increase the contact area between the idler bracket 2 and the end of the roller body 5, form four limiting points on the end of the roller body 5, and keep the roller body 5 axially stable between the two idler brackets 2.

[0029] Furthermore, to form sufficient linkage force for the two idler brackets 2, the telescopic linkage member is a linkage oil cylinder 21. The linkage oil cylinder 21 includes a cylinder body respectively hinged on the two idler brackets 2 and a telescopic rod moving in the cylinder body. The piston rod expands and contracts to make the two idler brackets 2 approach each other to a predetermined position. The hinge design can prevent the linkage oil cylinder 21 from jamming when it moves.

[0030] Furthermore, as Figure 6-7As shown, the linkage cylinder 21 and the pushing cylinder 3 need to be driven by hydraulic oil during operation. Therefore, the frame 1 in this embodiment is of a frame structure, and a hydraulic station 18 connected to both the linkage cylinder 21 and the pushing cylinder 3 through hydraulic oil pipes is provided inside the frame structure. The hydraulic station 18 can output hydraulic oil to drive the linkage cylinder 21 and the pushing cylinder 3 to act. The hydraulic station 18 is an existing hydraulic component, and its specific principle will not be elaborated here. Among them, there are a plurality of connected windows on the four side walls and the upper and lower end faces of the frame structure. The windows on the upper end face and the four side walls are connected and sealed by cover plates. The hydraulic oil pipes can penetrate into the lower windows close to the linkage cylinder 21 and the pushing cylinder 3 and be connected to the hydraulic station 18, ensuring the operation of the linkage cylinder 21 and the pushing cylinder 3 while optimizing the layout space.

[0031] Furthermore, the linkage cylinder 21 is not only a linkage member for the two roller seats 2 to approach or move away from each other, but also a connecting member between the two roller seats 2. The two roller seats 2 are connected by a telescopic linkage member to form a roller seat assembly that can move synchronously. Specifically, two guide rails spaced front and back are provided on the frame 1. A corresponding connecting seat 251 is installed at the upper end of the cross plate 25 of the roller seat 2, and a sliding sleeve is installed on the connecting seat 251. The sliding sleeve is slidably connected to the corresponding guide rail. To adjust the positions of the two roller seats 2 at any time so that the two roller seats 2 are symmetric about the lower brush roller as a reference during roll change, ensuring that the two roller assemblies can simultaneously support the circular bosses 51 at both ends of the roller barrel, as Figure 12 shown, a positioning assembly is provided between the frame 1 and the roller seat assembly. The positioning assembly includes an adjusting rack 231 and an adjusting gear 232 respectively provided on the frame 1 and the roller seat assembly. A control rod is installed on the adjusting gear 232, and a rotating shaft sleeve 252 is installed on the corresponding roller seat 2. The control rod is installed on the adjusting gear 232, the control rod is located inside the rotating shaft sleeve 252, and both ends of the control rod penetrate outside the rotating shaft sleeve 252. The inner end of the control rod is connected to the adjusting gear 252, and a control handwheel 23 exposed on the frame 1 is installed at the outer end of the control rod. After rotating the control handwheel 23 and driving the two roller seats 2 to move synchronously in the left-right direction and stop at the corresponding positions, before roll change, the two roller seats 2 are symmetric about the lower brush roller as a reference, avoiding the phenomenon that one end of the roller body 5 of the lower brush roller is supported and the other end is not supported.

[0032] Furthermore, as Figure 16As shown, in an ideal state, after the two opposing supporting members 22 are in place as the roller support base 2 moves, the supporting members 22 should be aligned with the roller body 5 and closely adhere to the outer peripheral position of the circular boss 51. However, due to errors, it is difficult to ensure the absolute accuracy of the position of the supporting members 22. Therefore, to avoid interference between the supporting members 22 and the roller body 5 of the lower brush roller when the supporting members 22 move, when the two roller support bases 2 approach each other to a predetermined position, a preset gap s is formed between the supporting members 22 and the roller body 5 of the lower brush roller; this preset gap s allows the supporting members 22 not to collide and interfere with the circular boss 51 after moving into place; but the preset gap s left will make it difficult for the supporting members 22 to contact the circular boss 51 on the roller body 5. Therefore, a gap compensation assembly 4 is also provided on the frame 1. The gap compensation assembly 4 includes a driving assembly and a transmission assembly 43. The transmission assembly 43 includes a transmission wheel 432 for being arranged on the frame 1. A connecting rod 433 is provided between the transmission wheel 432 and the lifting member. The lifting member is a lifting plate 434. The lower end of the connecting rod 433 is hinged to the lifting member, and the upper end of the connecting rod 433 is eccentrically rotationally connected to the transmission wheel 432; the driving assembly can drive the transmission wheel 432 to synchronously rotate a predetermined angle and drive the lifting member to extend downward by a predetermined length to act on the bearing seat, so as to lift the frame 1 and the two roller support bases 2 upward by a predetermined height; the eccentric connection causes the entire connecting rod 433 to generate a displacement in the longitudinal direction when the transmission wheel 432 rotates, driving the lifting member to extend downward and act on the bearing seat 1a; thus forming an upward reaction force on the frame 1 to lift the frame 1 by a predetermined height. The size of the predetermined height is the size of the preset gap s. After eliminating the preset gap s, the supporting members 22 can closely adhere to the outer periphery of the circular boss 51 and form a support for the roller body 5.

[0033] Furthermore, to make the downward movement of the lifting plate 434 more stable and smooth, a lifting guiding assembly is provided between the frame 1 and the lifting plate 434. The lifting guiding assembly includes two opposing guiding blocks arranged on the frame 1, and guiding plates 435 arranged at the front and rear ends of the lifting plate 434. The guiding plates 435 are made of plastic; the two guiding blocks form a guiding groove, and the two guiding plates 435 are in contact with the corresponding inner walls of the guiding groove and can move up and down to guide the lifting plate 434 in its movement.

[0034] Furthermore, the driving component needs to satisfy the requirement of simultaneously driving two sets of front and rear opposite transmission wheels 432 in the two eccentric adjustment components to rotate simultaneously. To meet this requirement, the transmission wheel 432 is a transmission gear, the transmission component 43 includes two front and rear opposite transmission gears, the number of connecting rods 433 corresponds to the number of transmission gears, the driving component includes a driving shaft 41 and two driving gears 431, and a linkage rod 439 is connected between the two driving gears 431 on the left and right sides; the corresponding driving gear 431 meshes with two front and rear opposite transmission gears on the left or right side simultaneously; the driving shaft 41 acts directly or indirectly on one of the driving gears 431, and an adjusting handwheel 411 is connected to the outer end of the driving shaft 41. By rotating the adjusting handwheel 411, multiple transmission gears are rotated by a predetermined angle and stopped at corresponding positions.

[0035] Furthermore, in an ideal state, the driving shaft 41 can be directly connected to one of the driving gears 431. However, to prevent the lifting plate 434 from accidentally resetting upward and causing the preset gap s to appear again, in this embodiment, the driving shaft 41 acts indirectly on one of the driving gears 431. Specifically, a self-locking transmission member is provided between the driving shaft 41 and the corresponding driving gear 431. The self-locking transmission member is a worm and worm gear transmission box 42. Inside the worm and worm gear transmission box 42, there is a worm and a worm gear that are in transmission connection. Its specific structure is similar to that in a worm and worm gear reducer, which belongs to the prior art and will not be elaborated here; the worm and worm gear transmission box 42 has an input end and an output end, and an output shaft 438 is provided at the output end position. The driving shaft 41 is connected to the input end of the worm and worm gear transmission box 42, and the corresponding driving gear 431 is connected to the output shaft 438 at the output end of the worm and worm gear transmission box 42; after the driving gear 431 rotates to the in-place position, due to the self-locking characteristic of the worm and worm gear, the worm and worm gear transmission box 42 restricts the driving gear 431 from rotating in the reverse direction, so that the two transmission wheels 432 stop at the predetermined positions; preventing the transmission wheels from reversing and keeping the lifting member in the downward extended state.

[0036] Furthermore, the eccentric rotational connection structure between the transmission wheel 432 and the connecting rod 433 is as follows: a central hole 432b is provided in the middle of the transmission wheel 432, a rotating shaft hole is provided at the upper end of the connecting rod 433, and an eccentric component is installed in the rotating shaft hole. The eccentric component includes a transmission shaft 432a and an eccentric sleeve 436. An eccentric hole 4361 that is not concentric with the rotating shaft hole is provided on the eccentric sleeve 436. The transmission shaft 432a is inserted into the eccentric hole 4361 and the central hole 432b, and is circumferentially fixed to the eccentric sleeve 436 and the transmission wheel 432; the transmission wheel 432 rotates to drive the two lifting plates 434 to extend downward; while the eccentric sleeve 436 can form an eccentric drive for the connecting rod 433, it can ensure uniform stress distribution of the transmission wheel 432.

[0037] Furthermore, an eccentricity is formed between the center of the eccentric hole 4361 and the center of the rotating shaft hole. Considering the variation in the outer diameter of the roller body 51 of the lower brush roller of different specifications, the range of the eccentricity in this embodiment is 3 mm - 12 mm. To facilitate determining whether the preset gap s is eliminated in place, the magnitude of the eccentricity in this embodiment is equal to half of the predetermined height. And the predetermined angle for the synchronous rotation of the plurality of transmission wheels 432 is 180 degrees. In the initial state, the center of the rotating shaft hole is directly above the center of the central hole 432b. When the plurality of transmission wheels 432 rotate synchronously by 180 degrees, the center of the rotating shaft hole moves to directly below the center of the central hole 432b, and the center of the rotating shaft hole moves a distance equal to twice the eccentricity in the vertical direction, which is the same as the magnitude of the predetermined height and also the same as the width of the preset gap s. For example, when the width of the preset gap s is 10 mm and the magnitude of the eccentricity is 5 mm, in the initial state, the center of the rotating shaft hole of the connecting rod 433 is located at the uppermost end of the central hole. At this time, by controlling the transmission wheel 432 to rotate 180°, the preset gap s can be eliminated in place.

[0038] Furthermore, this design can also ensure that the roller shaft of the lower brush roller will not be deformed. Specifically, when the preset gap s is eliminated, the supporting surface 221 of the supporting member 22 has contacted the circular boss 51 of the roller body 5. However, if the eccentricity is greater than the width of the preset gap s, when the worker accidentally exceeds the predetermined angle when rotating the control handwheel 41, an upward acting force will be formed on the roller body 5, resulting in deformation of the roller shaft stuck in the sliding seat 14 and the fixed seat 15. For example, when the width of the preset gap s is 10 mm and the magnitude of the eccentricity is also 10 mm, only by rotating the entire transmission wheel 432 by 90° can the preset gap s be eliminated. When the operator accidentally exceeds the rotation angle of the transmission wheel 432 by more than 90°, the lifting plate 434 will continue to move downward and press against the bearing seat 1a, causing slight deformation of the roller shaft and affecting the service life of the lower brush roller. However, this situation will not occur with the eccentricity in this embodiment. In this embodiment, when the preset gap s is eliminated in place, the center of the rotating shaft hole is already located at the lowermost position of the center of the central hole. When the angle of synchronous rotation of the plurality of transmission wheels 432 is greater than 180 degrees, the center of the rotating shaft hole rotates around the center of the central hole 432b and approaches the initial position, driving the two already downward-extended lifting plates 434 to reset upward. Even if the rotation angle of the transmission wheel 432 is accidentally exceeded by more than 180°, it will not cause an excessive acting force of the supporting member 22 on the roller body 5, ensuring the structural strength and service life of the lower brush roller.

[0039] Furthermore, to facilitate the operator to confirm whether the preset gap s is eliminated, as Figure 10As shown, the outer end of one of the transmission shafts 432a is connected to a pointer 412 exposed on the frame 1, and a dial 413 corresponding to the position of the pointer 412 is provided on the frame 1, and a plurality of scale values ​​are evenly distributed along the circumference on the dial 413: the scale value is usually an angle value. For example, when the width of the preset gap s is 10mm and the size of the eccentricity is 5mm, an angle value of 0-180° can be set on the dial 413; after the transmission shaft 432a rotates a corresponding angle and stops at a corresponding position, the scale value variation range of the pointer 412 on the dial 413 is visually inspected, that is, whether the pointer 412 is visually inspected to see if it has rotated 180°, to confirm that the preset gap s between the supporting member 22 and the roller body 5 has been eliminated.

[0040] Furthermore, the eccentric hole 4361 and the transmission shaft 432a, and the center hole and the transmission shaft 432a are connected by keys so that the transmission wheel 432 and the eccentric sleeve are circumferentially fixed to the transmission shaft 432a; the key connection can be a flat key connection or a spline connection.

[0041] Further, if Figure 9 As shown, in an ideal state, the transmission shaft 432a always maintains a concentric state with the eccentric hole 4361 when rotating. However, due to manufacturing and installation errors, a slight relative displacement will be generated in the lateral direction with the eccentric hole 4361 when the transmission shaft 432a rotates, which is the so-called misalignment phenomenon. In order to prevent the misalignment phenomenon from generating a lateral force on the connecting rod 433 and affecting the smooth movement of the connecting rod 433, a spherical bearing 437 is installed in the rotating shaft hole, and the spherical bearing 437 is sleeved on the outer wall of the eccentric sleeve 436; the contact surface between the inner ring and the outer ring of the spherical bearing 437 is spherical, and its inner ring is sleeved on the outer wall of the eccentric sleeve 436. While ensuring the smooth rotation of the transmission shaft 432a in the circumferential direction, the connecting rod 433 is allowed to swing relative to the transmission shaft 432a in the lateral direction to avoid excessive lateral force on the connecting rod 433.

[0042] Furthermore, end covers are provided at both ends of the shaft hole of the connecting rod 433 to seal the shaft hole, thereby ensuring that the components in the shaft hole are isolated from the outside world. The end covers can also limit the movement of the joint bearing 437. Specifically, two retaining ring grooves 4362 corresponding to the positions of the two ends of the joint bearing 437 are provided on the outer wall of the eccentric sleeve 436. Retaining rings are provided in the retaining ring grooves 4362. The two retaining rings are respectively supported by two end covers to limit the axial movement of the joint bearing 437.

[0043] Furthermore, the position where the eccentric sleeve 436 sets the joint bearing 437 also has an annular groove 4363, which can contain lubricant to make the rotation of the transmission shaft 432a smoother, and can also serve as an installation mark so that the joint bearing 437 can be quickly installed in place.

[0044] Example 2: Figure 17As shown in the figure, the difference between this embodiment and the above-mentioned embodiment is that the gap compensation component in this embodiment includes two lifting cylinders 6 that are spaced front and back and arranged on the left and right sides of the frame 1. The lifting member is a lifting rod that telescopically moves longitudinally inside the lifting cylinder 6. Connect the four lifting cylinders 6 on the frame 1 to the hydraulic station 18, so that the four lifting rods can move downward simultaneously to act on the bearing seat 1a, thereby achieving the same lifting effect on the entire frame 1 and the roller seat 2 as in the above-mentioned embodiment.

[0045] Embodiment 3: As Figure 18 shown in the figure, the difference between this embodiment and the above-mentioned embodiment is that the gap compensation component in this embodiment includes screws 7 arranged on the left and right sides of the frame 1. The lifting member is a lifting inner screw sleeve 72 threadedly connected to the lower end of the screw 7. A handle 71 is connected to the outer wall of the lifting inner screw sleeve. Rotate the handle 71 to make the lifting inner screw sleeve 72 rotate circumferentially and extend downward. During operation, two operators can simultaneously rotate the handles 71 on the left and right sides of the frame 1, so that the lifting inner screw sleeve 72 rotates along the vertical axis and moves downward at the same time, thereby achieving the same lifting effect on the entire frame 1 and the roller seat 2 as in the above-mentioned embodiment.

[0046] The above schematically describes the present invention and its implementation manners. This description is not restrictive. What is shown in the drawings is only one of the implementation manners of the present invention, and the actual structure is not limited thereto. Therefore, if those of ordinary skill in the art are inspired by it and, without departing from the purpose of the present invention's creation, design structures and embodiments similar to this technical solution without creative efforts, they shall fall within the protection scope of the present invention.

Claims

1. A roller changing mechanism with gap compensation function, characterized in that: The invention comprises a frame (1) for being placed on the upper end of a bearing seat (1a); the lower end of the frame (1) is slidably connected to two left-right symmetrical roller seats (2); the roller seats (2) comprise two front-to-back opposing support parts (24); a clearance groove (241) with an open lower end and for avoiding a roller shaft is provided between the two support parts (24); a supporting member (22) is provided inside the support part (24); the two front-to-back opposing support members (22) constitute a roller assembly for supporting a roller body (5) of a lower brush roller; a gap compensation assembly (4) is provided on both left and right sides of the frame (1); the gap compensation assembly (4) comprises a lifting member movable in the longitudinal direction; When the two roller seats (2) slide in the left-right direction and drive the two roller assemblies to approach each other to a predetermined position, a preset gap (s) is formed between each supporting member (22) and the roller body (5). At this time, the lifting member can move downward to act on the bearing seat (1a), thereby lifting the frame (1) and the two roller seats (2) upward to a predetermined height, so as to eliminate the preset gap (s) and make the supporting member (22) and the roller body (5) close to each other.

2. The roller changing mechanism with gap compensation function according to claim 1, characterized in that: The clearance compensation assembly (4) comprises a driving assembly and a transmission assembly (43), wherein the transmission assembly (43) comprises a transmission wheel (432) for being arranged on the frame (1), wherein a connecting rod (433) is arranged between the transmission wheel (432) and the lifting member, wherein the lower end of the connecting rod (433) is hinged on the lifting member, and the upper end of the connecting rod (433) forms an eccentric rotation connection with the transmission wheel (432); the driving assembly can drive the transmission wheel (432) to rotate synchronously by a predetermined angle, and drive the lifting member to extend downward by a predetermined length to act on the bearing seat, thereby lifting the frame (1) and the two roller seats (2) upward by a predetermined height.

3. The roller changing mechanism with gap compensation function according to claim 2, characterized in that: The transmission wheel (432) is a transmission gear. The transmission assembly (43) includes two transmission gears that are opposite to each other in front and back. The number of connecting rods (433) corresponds to the number of transmission gears. The driving assembly includes a driving shaft (41) and two driving gears (431). A linkage rod (439) is connected between the two driving gears (431) on the left and right sides. The corresponding driving gear (431) is simultaneously meshed with the two transmission gears that are opposite to each other in front and back on the left or right sides. The driving shaft (41) directly or indirectly acts on one of the driving gears (431). An adjusting hand wheel (411) is connected to the outer end of the driving shaft (41). The adjusting hand wheel (411) is rotated to rotate the plurality of transmission gears to a predetermined angle and stop at a corresponding position.

4. The roller changing mechanism with gap compensation function according to claim 3, characterized in that: A self-locking transmission member is provided between the drive shaft (41) and the corresponding drive gear (431), and the self-locking transmission member is a worm gear transmission box (42). The drive shaft (41) is connected to an input end of the worm gear transmission box (42), and the corresponding drive gear (431) is connected to an output end of the worm gear transmission box (42). After the drive gear (431) rotates to a certain position, the worm gear transmission box (42) restricts the drive gear (431) from rotating in the opposite direction, so that the two drive wheels (432) stop at a predetermined position.

5. The roller changing mechanism with gap compensation function according to claim 2, characterized in that: A center hole (432b) is provided in the middle of the transmission wheel (432), a rotating shaft hole is provided at the upper end of the connecting rod (433), an eccentric assembly is installed in the rotating shaft hole, and the eccentric assembly comprises a transmission shaft (432a) and an eccentric sleeve (436), an eccentric hole (4361) which is not concentric with the rotating shaft hole is provided on the eccentric sleeve (436), the transmission shaft (432a) is passed through the eccentric hole (4361) and the center hole (432b), and is circumferentially fixed to the eccentric sleeve (436) and the transmission wheel (432); the transmission wheel (432) rotates to drive the lifting member to extend downward.

6. The roller changing mechanism with gap compensation function according to claim 5, characterized in that: An eccentric distance is formed between the center of the eccentric hole (4361) and the center of the rotating shaft hole, and the size of the eccentric distance is equal to one-half of the predetermined height; and the predetermined angle of rotation of the transmission wheel (432) is 180 degrees; in the initial state, the center of the rotating shaft hole is located directly above the center of the center hole (432b); when the multiple transmission wheels (432) rotate 180 degrees synchronously, the center of the rotating shaft hole moves to directly below the center of the center hole (432b).

7. The roller changing mechanism with gap compensation function according to claim 6, characterized in that: When the transmission wheel (432) rotates at an angle greater than 180 degrees, the center of the rotating shaft hole rotates around the center of the central hole (432b) and approaches the initial position, and drives the lifting member that has extended downward to reset upward.

8. The roller changing mechanism with gap compensation function according to claim 1, characterized in that: The clearance compensation component (4) comprises two lifting cylinders (6) spaced apart from each other and arranged on the left and right sides of the frame (1), wherein the lifting member is a lifting rod that is telescopic in the longitudinal direction inside the lifting cylinder (6).

9. The roller changing mechanism with gap compensation function according to claim 1, characterized in that: The clearance compensation assembly (4) comprises a screw rod (7) arranged on the left and right sides of the frame (1); the lifting member is a lifting inner screw sleeve (72) threadedly connected to the lower end of the screw rod (7); a handle (71) is connected to the outer wall of the lifting inner screw sleeve; the handle (71) is turned to cause the lifting inner screw sleeve (72) to rotate in the circumferential direction and extend downward.

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