A roll changing mechanism with gap compensation function

Abstract

The application discloses a roll changing mechanism with a gap compensation function, which comprises a rack used for being placed on the upper end of a bearing seat, two left-right symmetrical supporting roller seats which are slidably connected to the lower end of the rack in the left-right direction, the supporting roller seat comprising two front-rear opposite supporting parts, the two supporting parts being provided with an avoiding groove which is open at the lower end and avoids the roller shaft, the inner side of the supporting part being provided with a supporting piece, the two front-rear opposite supporting pieces constituting a supporting roller assembly used for supporting the roller body of a lower brush roller, the left and right sides of the rack being provided with gap compensation assemblies, and the gap compensation assembly comprising a lifting piece which can move in the longitudinal direction.

Description

Technical Field

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

[0002] After the steel plate is manufactured, it is rolled up and stored as a steel coil. The steel coil will then go to the processing plant and be made into parts. During the period from when the steel plate enters the processing plant to when it is cut, the surface material of the steel plate is prone to peeling or corrosion. In order to remove the corrosion layer, the steel plate needs to be polished by the upper and lower brush rollers that are opposite each other in the steel plate polishing equipment. Both the upper and lower brush rollers include a roller body and roller shafts located at both ends of the roller body. After a long period of polishing, the polishing effect of the brush rollers will also decrease, so the brush rollers need to be replaced.

[0003] When replacing the upper brush roller, the roller changing trolley can be driven into the brush grinding equipment for receiving and replacement. However, the lower brush roller can usually only be replaced manually. For example, in the oxide scale treatment device with announcement number CN216371592, there are two bearing seats on the support seat. One of the bearing seats is slidable, and the other is fixed. They can be regarded as a sliding seat and a fixed seat, respectively. The roller shafts at both ends of the lower brush roller are respectively inserted into the sliding seat and the fixed seat. When changing the roller, the support seat needs to be moved out of the equipment, and then the worker needs to use a sling to suspend the roller body of the lower brush roller so that the sliding seat and the fixed seat are disengaged from the roller shafts at both ends of the lower brush roller. However, the force of the sling is difficult to control, and the lower brush roller is prone to deflection, which causes the roller shaft stuck in the bearing seat to deform. The operation is difficult and the roller changing efficiency is low.

[0004] The applicant designed a mechanism for changing rollers from the upper end of a support base, including a frame that can be hoisted onto the upper end of the support base. The lower end of the frame is provided with two roller seats that are slidably connected to the frame. Each roller seat includes two front-to-back opposing support parts. Between the two support parts is a clearance groove with an open lower end that avoids the roller shaft. The inner side of the support part has a support member. The two front-to-back opposing support members constitute a roller support assembly. When the two roller seats approach each other and the two roller support assemblies support the roller body of the lower brush roller, the lower brush roller remains stable. At this time, the sliding seat and the fixed seat can be disengaged from the two ends of the lower brush roller respectively, and the roller shaft of the lower brush roller remains unchanged.

[0005] However, the design difficulty lies in the fact that the support component is difficult to fit snugly against the roller body of the lower brush roller. Ideally, when the two roller seats are close to each other, each support component should be tightly attached to the roller body of the lower brush roller. However, in reality, due to manufacturing and installation errors, there will always be a slight deviation in the installation position of the support component, making it difficult to fit snugly against the roller body. If the front and rear distance of the two support components is too close, the support component will also collide and interfere with the roller. Therefore, to avoid this phenomenon, the distance between the two front and rear opposing support components needs to be wider so that after the two roller seats are moved into place, a pre-set gap is formed between the support component and the roller body. However, after leaving the pre-set gap, the support component separates from the roller body. 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, which is stuck in the fixed seat, will still deform. Summary of the Invention

[0006] This invention provides a roller changing mechanism with gap compensation function. By setting gap compensation components on the left and right sides of the frame, the longitudinally movable lifting component moves downward to press against the support seat and then raises the frame upward to a predetermined height. While eliminating the preset gap, the support component is made to fit with the roller body, which prevents the lower brush roller shaft from deforming when it detaches from the roller seat, thereby improving the service life of the lower brush roller and the roller changing efficiency.

[0007] The technical solution of this invention is implemented as follows:

[0008] A roller changing mechanism with gap compensation function includes a frame for placing on the upper end of a support seat. Two symmetrical roller seats are slidably connected to the lower end of the frame in the left-right direction. Each roller seat includes two front-to-back opposing support parts. There is a clearance groove between the two support parts with the lower end open and avoiding the roller shaft. There are support members inside the support parts. The two front-to-back opposing support members constitute a roller assembly for supporting the roller body of the lower brush roller. Gap compensation components are provided on both the left and right sides of the frame. The gap compensation components include lifting members that can move longitudinally.

[0009] When the two idler seats slide in the left and right direction and drive the two idler assemblies to approach each other to a predetermined position, a preset gap is formed between each support and the roller body. At this time, the lifting component can move downward to act on the bearing seat, thereby raising the frame and the two idler seats upward to a predetermined height, so as to eliminate the preset gap and make the support and the roller body fit tightly.

[0010] Preferably, the gap compensation assembly includes a drive assembly and a transmission assembly. The transmission assembly includes a drive wheel mounted on the frame, and a connecting rod between the drive wheel and the lifting member. The lower end of the connecting rod is hinged to the lifting member, and the upper end of the connecting rod forms an eccentric rotational connection with the drive wheel. The drive assembly can drive the drive wheel to rotate synchronously by a predetermined angle, and cause the lifting member to extend downward by a predetermined length to act on the bearing seat, thereby raising the frame and the two idler roller seats upward by a predetermined height. The eccentric connection causes the entire connecting rod to displace longitudinally when the drive wheel rotates, causing the lifting member to extend downward and act on the bearing seat.

[0011] Preferably, the transmission wheel is a transmission gear, the transmission assembly includes two front-to-back transmission gears, the number of connecting rods corresponds to the number of transmission gears, the drive assembly includes a drive shaft and two drive gears, and a linkage rod connects the two drive gears on the left and right sides; the corresponding drive gear meshes with the two front-to-back transmission gears on the left or right side simultaneously; the drive shaft acts directly or indirectly on one of the drive gears, and an adjusting handwheel is connected to the outer end of the drive shaft. Rotating the adjusting handwheel causes multiple transmission gears to rotate a predetermined angle and stop at the corresponding position.

[0012] Preferably, a self-locking transmission component is provided between the drive shaft and the corresponding drive gear. The self-locking transmission component is a worm gear transmission box. The drive shaft is connected to the input end of the worm gear transmission box, and the corresponding drive gear is connected to the output end of the worm gear transmission box. After the drive gear rotates to the correct position, the worm gear transmission box restricts the drive gear from rotating in the opposite direction, so that the two transmission wheels stop at the predetermined position. This prevents the transmission wheels from reversing and keeps the lifting component in the downward extended state.

[0013] Preferably, the transmission wheel has a central hole in the middle, and the connecting rod has a shaft hole at the upper end. An eccentric assembly is installed in the shaft hole. The eccentric assembly includes a transmission shaft and an eccentric sleeve. The eccentric sleeve has an eccentric hole that is not concentric with the shaft hole. The transmission shaft passes through the eccentric hole and the central hole and is circumferentially fixed with the eccentric sleeve and the transmission wheel. The transmission wheel rotates to drive the lifting component to extend downward. The eccentric sleeve can ensure uniform stress distribution of the transmission wheel while forming an eccentric transmission to the connecting rod.

[0014] Preferably, there is an eccentricity between the center of the eccentric hole and the center of the rotating shaft hole, and the size of the eccentricity is equal to half of the predetermined height; and the predetermined angle of synchronous rotation of the multiple transmission wheels is 180 degrees; in the initial state, the center of the rotating shaft hole is located directly above the center of the central hole; when the multiple transmission wheels rotate synchronously by 180 degrees, the center of the rotating shaft hole moves to directly below the center of the central hole.

[0015] Preferably, when the angle of synchronous rotation of multiple drive wheels is greater than 180 degrees, the center of the shaft hole rotates around the center of the central hole and moves closer to the initial position, driving the two lifting parts that have already extended downwards to return to their original positions; this prevents excessive rotation from causing the frame to be raised excessively and avoids the roller body from being subjected to upward force, which could lead to roller shaft deformation.

[0016] Preferably, the gap compensation assembly includes two lifting cylinders arranged on the left and right sides of the frame, and the lifting component is a lifting rod that extends and retracts longitudinally inside the lifting cylinder.

[0017] Preferably, the gap compensation component includes screws disposed on the left and right sides of the frame, and the lifting component is a lifting inner screw sleeve threaded to the lower end of the screw. A handle is connected to the outer wall of the lifting inner screw sleeve. Rotating the handle causes the lifting inner screw sleeve to rotate circumferentially and extend downward.

[0018] The beneficial effects of the present invention, which adopts the above technical solution, are as follows:

[0019] In this invention, gap compensation components are installed on the left and right sides of the lower end of the frame. When the support members on the two roller seats form a preset gap with the roller body of the lower brush roller, the lifting members therein move longitudinally to act on the support seat, raising the frame and the two roller seats to a predetermined height, thereby compensating for and eliminating the preset gap. This ensures that the support members provide just the right rigid support for the roller body, preventing the roller shaft from deforming when the lower brush roller detaches from the sliding seat and the fixed seat, and ensuring the quality of use of the lower brush roller and the efficiency of roller replacement. Attached Figure Description

[0020] Figure 1 This is a structural diagram of the roller changing mechanism;

[0021] Figure 2 This is a schematic diagram of the roller changing mechanism from another angle;

[0022] Figure 3 A cross-sectional view of the roller body supporting the lower brush roller, with two front and rear opposing support members.

[0023] Figure 4 This is a schematic diagram showing the roller changing mechanism positioned on the upper end of the support.

[0024] Figure 5 This is a schematic diagram showing the sliding seat disengaging from one end of the lower brush roller shaft after the lower brush roller body is supported.

[0025] Figure 6 A schematic diagram illustrating how the hydraulic cylinder is pushed to actuate and causes the roller shaft at the other end of the lower brush roller to disengage from the fixed seat;

[0026] Figure 7 The structural diagram of the clearance compensation component is shown below, with the frame concealed.

[0027] Figure 8 This is a cross-sectional view of the gap compensation component;

[0028] Figure 9 This is an enlarged sectional view of the position where the upper end of the connecting rod mates with the drive shaft;

[0029] Figure 10 An enlarged view of the pointer and dial on the frame;

[0030] Figure 11 This is a schematic diagram of the eccentric sleeve structure;

[0031] Figure 12This is a schematic diagram of the positioning adjustment component;

[0032] Figure 13 A structural diagram showing how two idler rollers support the lower brush roller.

[0033] Figure 14 This is a schematic diagram of the idler roller seat structure;

[0034] Figure 15 A simplified diagram illustrating the principle of the roller changing mechanism performing roller changing at the upper end of the bearing seat;

[0035] Figure 16 A cross-sectional comparison of the case where the preset gap exists and the case where the preset gap is eliminated;

[0036] Figure 17 This is a schematic diagram of the gap compensation component in Example 2;

[0037] Figure 18 This is a schematic diagram of the gap compensation component in Example 3;

[0038] The attached figures are labeled as follows: 1-Frame, 1a-Bearing seat, 2-Idler roller seat, 3-Pushing cylinder, 4-Gap compensation assembly, 5-Roller body, 6-Lifting 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-Guide seat, 17-Guide wheel, 18-Hydraulic station, 21-Linkage cylinder, 22-Support component, 23-Control handwheel, 24-Support part, 25-Horizontal plate, 26-Mounting plate, 27-Reinforcing plate, 41-Drive shaft, 42-Worm gear transmission box, 43-Transmission assembly, 51-Circular boss, 71-Screw, 72-Lifting cylinder 221-Supporting surface, 222-Limiting surface, 231-Adjusting rack, 232-Adjusting gear, 241-Allowing groove, 242-Abutting surface, 251-Connecting seat, 252-Rotating sleeve, 261-Fixing plate, 411-Adjusting handwheel, 412-Pointer, 413-Digital dial, 431-Drive gear, 432-Transmission wheel, 432a-Transmission shaft, 433-Connecting rod, 434-Lifting plate, 435-Guide plate, 436-Eccentric sleeve, 4361-Eccentric hole, 4362-Retaining ring groove, 4363-Annular groove, 437-Spherical bearing, 438-Output shaft, 439-Linkage rod, s-Preset clearance. Detailed Implementation

[0039] To better understand the above-mentioned objectives, 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 embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0040] Many specific details are set forth in the following description in order to provide a full understanding of the invention. However, the invention may also be practiced in other ways different from those described herein, and therefore the scope of protection of the invention is not limited to the specific embodiments disclosed below.

[0041] This invention has multiple embodiments, the specific embodiments of which are as follows:

[0042] Example 1: As Figure 1-16 As shown, this embodiment provides a roller changing mechanism with gap compensation function. The roller changing mechanism is used to change rollers on the support assembly that holds the lower brush roller. The support assembly includes a support seat 1a and a sliding seat 14 and a fixed seat 15 disposed on the support seat 1a and used to hold the roller shafts at both ends of the lower brush roller. The sliding seat 14 can slide along the length direction of the lower brush roller. The sliding seat 14 and the fixed seat 15 are disposed in a box with an opening on one side on the support seat 1a.

[0043] In this embodiment, the roller changing mechanism with gap compensation function includes a frame 1 for placing on the upper end of the support seat 1a. The frame 1 is placed on the upper end of the box. The lower end of the frame 1 is slidably connected to two symmetrical roller seats 2. The roller seat 2 includes two front-to-back support parts 24. There is a clearance groove 241 between the two support parts 24 with the lower end open and avoiding the roller shaft. The inner side of the support part 24 has a support member 22. The two front-to-back support members 22 constitute a roller assembly for supporting the roller body 5 of the lower brush roller. Gap compensation components are provided on both the left and right sides of the frame 1. The gap compensation components include lifting members that can move longitudinally.

[0044] When the two idler roller seats 2 slide in the left and right direction and drive the two idler roller assemblies to approach each other to a predetermined position, a preset gap s is formed between each support member 22 and the roller body 5. At this time, the lifting member can move downward to act on the support seat 1a, thereby raising the frame 1 and the two idler roller seats 2 upward to a predetermined height, so as to eliminate the preset gap s and make the support member 22 close to the roller body 5.

[0045] Furthermore, a telescopic linkage is provided between the two idler roller seats 2 to drive the two idler roller seats 2 to move closer to each other; wherein the idler roller seat 2 facing the fixed seat 15 is provided with a telescopic pushing member; the idler roller seat 2 includes two support parts 24 that are opposite to each other and extend downward, and a support member 22 is connected to the inner side of 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 roller shaft positions at both ends of the lower brush roller respectively;

[0046] In operation, the telescopic linkage drives the two roller seats 2 to move closer to each other and moves the two sets of front and rear opposite support members 22 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 pusher extends and extends and acts on the fixed seat 15, causing the two roller seats 2 to slide 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.

[0047] Furthermore, the roller body 5 of the lower brush roller includes a roller for laying brush strips. The outer diameter of the roller is much larger than the outer diameter of the roller shaft. If the brush strips are not considered, the support member 22 can be supported on the roller. However, in order to avoid the support member 22 contacting the brush strips on the roller and causing the brush strips to deform, circular bosses 51 for setting the roller shaft are concentrically installed at both ends of the roller. The outer diameter of the circular bosses 51 is smaller than the outer diameter of the roller. After the two roller seats 2 approach each other to a predetermined position, in this embodiment, the support member 22 supports the roller body 5. This means that after the support member 22 moves into place with the roller seat 2, it supports the outer periphery of the circular bosses 51, ensuring that the brush strips of the lower brush roller are not deformed by the pressure of the support member 22.

[0048] Furthermore, in order to place the roller changing mechanism on the upper end of the support seat 1a, a hoisting method is adopted in this embodiment. The sling needs to be hoisted onto the hook of the crane first, and then the two ends of the sling are respectively hoisted onto the frame 1. In order to ensure that the hoisted roller changing mechanism is kept horizontal, the frame 1 is provided with a hoisting leveling component. The hoisting leveling component includes a first lifting lug 11 and a second lifting lug 12 that are horizontally opposite each other. The first lifting lug 11 is provided with a single first lifting hole 13, and the second lifting lug 12 is provided with multiple horizontally spaced second lifting holes 13a. One end of the flexible sling is hoisted into the first lifting hole 13, and the other end of the flexible sling is hoisted into one of the multiple second lifting holes 13a. That is to say, the operator can switch the hoisting end of the sling in the multiple 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 roller changing mechanism is kept horizontal.

[0049] Furthermore, to ensure that the roller changing mechanism is positioned correctly on the upper end of the support seat 1a, a front-rear guide mechanism and a left-right guide mechanism are provided between the frame 1 and the support seat 1a. The front-rear guide mechanism includes an elastic guide wheel 17 mounted on the frame 1 and a guide block mounted on the support seat 1a. The left-right guide mechanism includes a guide seat 16 mounted on the frame 1 and a guide column mounted on the support seat 1a. Through the cooperation of the elastic guide wheel 17 and the guide block, and the cooperation of the guide seat 16 and the guide column, the roller changing mechanism in the hoisting state can be guided to a stable position on the upper end of the support seat 1a. The specific structure of the front-rear guide mechanism and the left-right guide mechanism can be referred to the corresponding content in the roller device patent with publication number CN221821042, and will not be repeated here.

[0050] Furthermore, the structure of the idler roller seat 2 is as follows: The idler roller seat 2 includes a horizontal plate 25 for sliding connection to the frame 1. A support is connected to the lower end of the horizontal plate 25. The lower end of the support is recessed in the middle to form two front-to-back opposing support parts 24 and a clearance groove 241 between the two support parts 24. A longitudinal plate 26 is provided between the horizontal plate 25 and each support part 24. The longitudinal plate 26 is the carrier for mounting the linkage cylinder 21 and also strengthens the connection between the horizontal plate 25 and the support part 24. The aforementioned extension is connected between every two left-to-right opposing longitudinal plates 26. The linkage component is retracted to allow the front and rear ends of the roller seat 2 to move synchronously. Two connecting ears are provided at the head end of the piston rod and the tail end of the cylinder. The width between the two connecting ears is greater than the thickness of the longitudinal plate 26. To ensure that the hinge is in place, a fixed plate 261 is connected to the longitudinal plate 26. Hinges are machined on both the longitudinal plate 26 and the fixed plate 261. The fixed 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 ears, so that after the linkage cylinder 21 is hinged in place, the linkage cylinder 21 remains stable in the front and rear directions.

[0051] Furthermore, to ensure the structural strength of the idler seat 2, the idler seat 2 is a welded structural component, wherein the lower end of the horizontal plate 25 is provided with a support, and the middle position of the lower end of the support is recessed inward, thereby forming two support parts 24 and a clearance groove 241 located between the two support parts 24; to ensure the lightweight of the idler seat 2, the support is a hollow structure, including at least two vertical plates 243 that are spaced apart from each other and welded to the lower end of the horizontal plate 25, and the middle position of the lower end of the two vertical plates 243 is recessed inward, thereby forming two support parts 24 and a clearance groove 241 located between the two support parts 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 structure of the support.

[0052] Furthermore, such as Figure 13-14 As shown, to ensure the lower brush roller remains stable when it disengages from the sliding seat 14 and the fixed seat 15, the support member 22 is provided with an outwardly open support groove. 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 fit the circular boss 51 of the roller body 5, the support surface 221 is an arc-shaped surface. When the two roller 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 in contact with the outer end faces of the two circular bosses 51 respectively, the support member 22 can effectively prevent the lower brush roller from moving laterally.

[0053] Furthermore, the limiting surface 222 on the support member 22 has a small area, and there are only two support members 22 on each roller seat 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, in order to increase the stability of the roller body 5, the inner side of the support part 24 is provided with a contact plate for contacting the end face of the lower brush roller. The contact plate is provided with a contact surface 242. The contact surface 242 and the limiting surface 222 are on the same vertical plane to increase the contact area of ​​the roller seat 2 on the end of the roller body 5 and form four limiting points on the end of the roller body 5, so that the roller body 5 can maintain axial stability between the two roller seats 2.

[0054] Furthermore, in order to generate sufficient linkage force for the two idler roller seats 2, the telescopic linkage component is a linkage cylinder 21. The linkage cylinder 21 includes a cylinder body that is respectively hinged to the two idler roller seats 2 and a telescopic rod that moves within the cylinder body. The piston rod extends and retracts, bringing the two idler roller seats 2 closer to each other to a predetermined position. The hinged design can prevent the linkage cylinder 21 from jamming when it operates.

[0055] Furthermore, such as Figure 6-7 As shown, the linkage cylinder 21 and the push cylinder 3 require hydraulic oil to drive them during operation. Therefore, the frame 1 in this embodiment is a frame structure. The frame structure is equipped with a hydraulic station 18 that is connected to both the linkage cylinder 21 and the push cylinder 3 via hydraulic oil pipes. The hydraulic station 18 can output hydraulic oil to drive the linkage cylinder 21 and the push cylinder 3. The hydraulic station 18 is an existing hydraulic component, and its specific principle will not be described in detail. The frame structure has multiple connected windows on its four side walls and upper and lower end faces. The windows on the upper end face and four side walls are sealed by cover plates. The hydraulic oil pipes can pass through the lower end windows near the linkage cylinder 21 and the push cylinder 3 and connect to the hydraulic station 18, ensuring that the linkage cylinder 21 and the push cylinder 3 can move while optimizing the layout space.

[0056] Furthermore, the linkage cylinder 21 is not only a linkage component that moves the two idler roller seats 2 closer or further apart, but also a connecting component between the two idler roller seats 2; the two idler roller seats 2 are connected by a telescopic linkage component to form a synchronously movable idler roller seat assembly; specifically, the frame 1 is provided with two guide rails spaced apart front and rear, and a corresponding connecting seat 251 is installed on the upper end of the horizontal plate 25 of the idler roller seat 2. A sliding sleeve is installed on the connecting seat 251, and the sliding sleeve is slidably connected to the corresponding guide rail; in order to adjust the position of the two idler roller seats 2 at any time, so that the two idler roller seats 2 are symmetrical about left and right with the lower brush roller as the reference when changing rollers, and to ensure that the two idler roller assemblies can simultaneously support the circular bosses 51 at both ends of the roller, such as Figure 12As 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 mounted on the frame 1 and the roller seat assembly. A control rod is mounted on the adjusting gear 232, and a rotating sleeve 252 is mounted on the corresponding roller seat 2. The control rod is located inside the rotating sleeve 252, with both ends of the control rod extending out of the rotating sleeve 252. One end of the control rod is connected to the adjusting gear 252, and a control handwheel 23 exposed on the frame 1 is mounted on the outer end of the control rod. Rotating the control handwheel 23 drives the two roller seats 2 to move synchronously in the left and right directions and stop at the corresponding positions, so that before changing the roller, the two roller seats 2 are symmetrical about the left and right with the lower brush roller as the reference. This avoids the phenomenon that one end of the lower brush roller body 5 is supported while the other end is not.

[0057] Furthermore, such as Figure 16 As shown, ideally, after the two opposing support members 22 move into position with the roller seat 2, the support members 22 should be aligned with the roller body 5 and closely abut the outer periphery of the circular boss 51. However, due to error, the position of the support members 22 is difficult to guarantee absolute accuracy. Therefore, to avoid interference between the support members 22 and the roller body 5 of the lower brush roller when they move, a preset gap s is formed between the support members 22 and the roller body 5 of the lower brush roller when the two roller seats 2 move close to each other to a predetermined position. This preset gap s can prevent the support members 22 from colliding and interfering with the circular boss 51 after they move into position. However, the preset gap s makes it difficult for the support members 22 to contact the circular boss 51 on the roller body 5. Therefore, the frame 1 is also provided with a gap compensation component 4. The gap compensation component 4 includes a drive component and a transmission component 43. The transmission component 43 includes a transmission component for mounting on the frame 1. A connecting rod 433 is provided between the wheel 432, the transmission wheel 432 and the lifting component. The lifting component is a lifting plate 434. The lower end of the connecting rod 433 is hinged to the lifting component, and the upper end of the connecting rod 433 is eccentrically rotated with the transmission wheel 432. The drive assembly can drive the transmission wheel 432 to rotate synchronously by a predetermined angle and drive the lifting component to extend downward by a predetermined length to act on the bearing seat, thereby raising the frame 1 and the two idler roller seats 2 upward by a predetermined height. The eccentric connection causes the entire connecting rod 433 to be displaced longitudinally when the transmission wheel 432 rotates, driving the lifting component to extend downward and act on the bearing seat 1a. This forms an upward reaction force on the frame 1, raising the frame 1 to a predetermined height. The size of the predetermined height is the size of the preset gap s. After the preset gap s is eliminated, the support member 22 can closely adhere to the outer periphery of the circular boss 51 and support the roller body 5.

[0058] Furthermore, to make the downward movement of the lifting plate 434 more stable and smooth, a lifting guide assembly is provided between the frame 1 and the lifting plate 434. The lifting guide assembly includes two front-to-back guide blocks set on the frame 1, and guide plates 435 set at the front and rear ends of the lifting plate 434. The guide plates 435 are made of plastic. The two guides form a guide groove, and the two guide plates 435 contact the corresponding inner walls of the guide groove and can move up and down to guide the movement of the lifting plate 434.

[0059] Furthermore, the drive assembly needs to simultaneously drive two sets of front-to-back opposing transmission wheels 432 in the two eccentric adjustment assemblies to rotate simultaneously. To meet this requirement, the transmission wheel 432 is a transmission gear, the transmission assembly 43 includes two front-to-back opposing transmission gears, the number of connecting rods 433 corresponds to the number of transmission gears, the drive assembly includes a drive shaft 41 and two drive gears 431, and a linkage rod 439 connects the two drive gears 431 on the left and right sides; the corresponding drive gear 431 meshes with the two front-to-back opposing transmission gears on the left or right side simultaneously; the drive shaft 41 acts directly or indirectly on one of the drive gears 431, and an adjusting handwheel 411 is connected to the outer end of the drive shaft 41. Rotating the adjusting handwheel 411 causes multiple transmission gears to rotate a predetermined angle and stop at the corresponding position.

[0060] Furthermore, ideally, the drive shaft 41 could be directly connected to one of the drive gears 431. However, to prevent the lifting plate 434 from accidentally resetting upwards and causing the preset gap s to reappear, in this embodiment, the drive shaft 41 acts indirectly on one of the drive gears 431. Specifically, a self-locking transmission component is provided between the drive shaft 41 and the corresponding drive gear 431. The self-locking transmission component is a worm gear transmission box 42, which contains a worm wheel and a worm connected for transmission. Its specific structure is similar to that in a worm gear reducer. The existing technology will not be described in detail here; the worm gear transmission box 42 has an input end and an output end, and an output shaft 438 is provided at the output end. The drive shaft 41 is connected to the input end of the worm gear transmission box 42, and the corresponding drive gear 431 is connected to the output shaft 438 at the output end of the worm gear transmission box 42; after the drive gear 431 rotates to the position, due to the self-locking characteristic of the worm gear, the worm gear transmission box 42 restricts the drive gear 431 from rotating in the opposite direction, so that the two transmission wheels 432 stop at the predetermined position; preventing the transmission wheels from reversing, so that the lifting part is kept in the downward extended state.

[0061] Furthermore, the eccentric rotation connection structure between the transmission wheel 432 and the connecting rod 433 is as follows: the transmission wheel 432 has a central hole 432b in the middle, and the connecting rod 433 has a shaft hole at the upper end. An eccentric assembly is installed in the shaft hole. The eccentric assembly includes a transmission shaft 432a and an eccentric sleeve 436. The eccentric sleeve 436 has an eccentric hole 4361 that is not concentric with the shaft hole. The transmission shaft 432a passes through the eccentric hole 4361 and the central hole 432b, and is circumferentially fixed with the eccentric sleeve 436 and the transmission wheel 432. The transmission wheel 432 rotates to drive the two lifting plates 434 to extend downward. The eccentric sleeve 436 can ensure that the stress distribution of the transmission wheel 432 is uniform while forming an eccentric transmission to the connecting rod 433.

[0062] 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 different specifications of the lower brush roller, the eccentricity range in this embodiment is 3mm-12mm. To facilitate determining whether the preset gap s has been eliminated, the eccentricity in this embodiment is equal to half of the predetermined height. The predetermined angle of synchronous rotation of multiple transmission wheels 432 is 180 degrees. In the initial state, the center of the rotating shaft hole is located directly above the center of the central hole 432b. When multiple transmission wheels... When wheel 432 rotates 180 degrees synchronously, the center of the shaft hole moves directly below the center of the center hole 432b. The center of the shaft hole moves vertically by twice the eccentricity, which is the same as 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 10mm and the eccentricity is 5mm, the center of the shaft hole of connecting rod 433 is located at the top of the center hole in the initial state. At this time, controlling the transmission wheel 432 to rotate 180° will eliminate the preset gap s.

[0063] Furthermore, this design also ensures that the lower brush roller shaft will not deform. Specifically, after the preset gap s is eliminated, the supporting surface 221 of the support 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, and the operator accidentally exceeds the predetermined angle when rotating the control handwheel 41, it will exert an upward force on the roller body 5, causing the roller shaft stuck in the sliding seat 14 and the fixed seat 15 to deform. For example, when the width of the preset gap s is 10mm and the size of the eccentricity is also 10mm, it is only necessary to rotate the entire transmission wheel 432 by 90° to eliminate the preset gap s. When the operator accidentally rotates the transmission wheel 432 by more than 90°, the lifting plate 434 will still... The roller will continue to move downwards and press against the support 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 when using the eccentricity in this embodiment. In this embodiment, after the preset gap s is eliminated, the center of the shaft hole is already located at the bottom of the center of the central hole. When the angle of synchronous rotation of multiple transmission wheels 432 is greater than 180 degrees, the center of the shaft hole rotates around the center of the central hole 432b and moves closer to the initial position, driving the two lifting plates 434 that have been extended downwards to reset upwards. Even if the rotation angle of the transmission wheel 432 is mistakenly made to exceed 180 degrees, it will not cause the support 22 to exert excessive force on the roller body 5, thus ensuring the structural strength and service life of the lower brush roller.

[0064] Furthermore, to facilitate operator confirmation of whether the preset gap s has been eliminated, such as... Figure 10 As shown, one of the drive shafts 432a has a pointer 412 exposed on the frame 1 at its outer end. The frame 1 is provided with a scale 413 corresponding to the position of the pointer 412. The scale 413 has multiple scale values ​​evenly distributed along the circumference. The scale values ​​are usually angle values. 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 scale 413. After the drive shaft 432a rotates to the corresponding angle and stops at the corresponding position, the range of change of the scale value of the pointer 412 on the scale 413 is visually observed, that is, whether the pointer 412 has rotated 180°, to confirm that the preset gap s between the support 22 and the roller 5 has been eliminated.

[0065] Furthermore, the eccentric hole 4361 and the drive shaft 432a, and the center hole and the drive shaft 432a are connected by keys to keep the drive wheel 432 and the eccentric sleeve circumferentially fixed to the drive shaft 432a; the key connection can be a flat key connection or a spline connection.

[0066] Furthermore, such as Figure 9As shown, ideally, the drive shaft 432a should always be concentric with the eccentric hole 4361 when it rotates. However, due to manufacturing and installation errors, the drive shaft 432a will have a slight relative displacement with the eccentric hole 4361 in the lateral direction when it rotates, which is called misalignment. To avoid the misalignment from causing a lateral force on the connecting rod 433 and affecting the smoothness of the connecting rod 433's movement, a spherical bearing 437 is installed in the shaft hole of the rotating shaft. The spherical bearing 437 is fitted on the outer wall of the eccentric sleeve 436. The contact surface between the inner and outer rings of the spherical bearing 437 is spherical. The inner ring is fitted on the outer wall of the eccentric sleeve 436. While ensuring that the drive shaft 432a rotates smoothly in the circumferential direction, the connecting rod 433 is allowed to swing relative to the drive shaft 432a in the lateral direction, thus avoiding excessive lateral force on the connecting rod 433.

[0067] Furthermore, the connecting rod 433 has end caps at both ends of the shaft hole to seal the shaft hole, ensuring that the components inside the shaft hole are isolated from the outside. The end caps can also restrict the movement of the spherical bearing 437. Specifically, the outer wall of the eccentric sleeve 436 has two retaining ring grooves 4362 corresponding to the positions of the two ends of the spherical bearing 437. The retaining rings are installed in the retaining ring grooves 4362, and the two retaining rings are respectively abutted by the two end caps to restrict the spherical bearing 437 from moving axially.

[0068] Furthermore, the eccentric sleeve 436, where the spherical bearing 437 is located, also has an annular groove 4363. The annular groove 4363 can accommodate lubricant, making the rotation of the drive shaft 432a smoother. It can also serve as an installation mark, allowing the spherical bearing 437 to be quickly installed in place.

[0069] Example 2: Figure 17 As shown, the difference between this embodiment and the above embodiment is that the gap compensation component in this embodiment includes lifting cylinders 6 arranged on the left and right sides of the frame 1. The lifting component is a lifting rod that extends and retracts longitudinally inside the lifting cylinder 6. By connecting the four lifting cylinders 6 on the frame 1 to the hydraulic station 18, the four lifting rods can move downwards simultaneously to act on the bearing seat 1a, thereby achieving the same lifting effect on the entire frame 1 and roller seat 2 as in the above embodiment.

[0070] Example 3: As Figure 18 As shown, this embodiment differs from the above embodiments in that the gap compensation component in this embodiment includes screws 7 disposed on the left and right sides of the frame 1, and the lifting component is a lifting inner screw sleeve 72 threadedly connected to the lower end of the screws 7. A handle 71 is connected to the outer wall of the lifting inner screw sleeve. Rotating the handle 71 causes the lifting inner screw sleeve 72 to 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, causing the lifting inner screw sleeve 72 to move downward while rotating along the vertical axis, thereby achieving the same lifting effect on the entire frame 1 and roller seat 2 as in the above embodiments.

[0071] The present invention and its embodiments have been described above illustratively. This description is not restrictive, and the figures shown are only one embodiment of the present invention; the actual structure is not limited thereto. Therefore, if those skilled in the art are inspired by this description and design similar structures and embodiments without departing from the spirit of the present invention, such designs should fall within the protection scope of the present invention.

Claims

1. A roller changing mechanism with gap compensation function, characterized in that, The system includes a frame (1) for placement on the upper end of a support base (1a). Two symmetrical roller supports (2) are slidably connected to the lower end of the frame (1) in the left-right direction. Each roller support (2) includes two opposing front-to-back support parts (24). A clearance groove (241) with an open lower end and clearance for the roller shaft is located between the two support parts (24). Support members (22) are located inside the support parts (24). The two opposing front-to-back support members (22) constitute a roller assembly for supporting the roller body (5) of the lower brush roller. Gap compensation components (4) are provided on both the left and right sides of the frame (1). Each gap compensation component (4) includes a lifting member that can move longitudinally. The gap compensation component (4) includes a drive assembly and a transmission assembly (43). The transmission assembly (43) includes a drive wheel (432) mounted on the frame (1). A connecting rod (433) is provided between the drive wheel (432) and the lifting member. The lower end of the connecting rod (433) is hinged to the lifting component, and the upper end of the connecting rod (433) is eccentrically connected to the transmission wheel (432). The transmission wheel (432) has a central hole (432b) in the middle, and the upper end of the connecting rod (433) has a shaft hole. An eccentric component is installed in the shaft hole. The eccentric component includes a transmission shaft (432a) and an eccentric sleeve (436). The eccentric sleeve (436) has an eccentric hole (4361) that is not concentric with the shaft hole. The transmission shaft (432a) passes through the eccentric hole (4361) and the central hole (432b) and is circumferentially fixed with the eccentric sleeve (436) and the transmission wheel (432). The transmission wheel (432) rotates to drive the lifting component to extend downward. The drive component can drive the transmission wheel (432) to rotate synchronously by a predetermined angle and drive the lifting component to extend downward by a predetermined length to act on the bearing seat, thereby raising the frame (1) and the two roller seats (2) upward to a predetermined height. Alternatively, the gap compensation component (4) may also include lifting cylinders (6) disposed on the left and right sides of the frame (1), wherein the lifting component is a lifting rod that extends and retracts longitudinally within the lifting cylinder (6); Alternatively, the gap compensation component (4) also includes screws (7) set on the left and right sides of the frame (1), and the lifting component is a lifting inner screw sleeve (72) threaded to the lower end of the screw (7). A handle (71) is connected to the outer wall of the lifting inner screw sleeve. Rotating the handle (71) causes the lifting inner screw sleeve (72) to rotate circumferentially and extend downward. When the two idler roller seats (2) slide in the left and right direction and drive the two idler roller assemblies to approach each other to a predetermined position, a preset gap (s) is formed between each support (22) and the roller body (5). At this time, the lifting component can move downward to act on the support seat (1a), thereby raising the frame (1) and the two idler roller seats (2) upward to a predetermined height, so as to eliminate the preset gap (s) and make the support (22) and the roller body (5) stick together.

2. The roller changing mechanism with gap compensation function according to claim 1, characterized in that: The transmission wheel (432) is a transmission gear, the transmission assembly (43) includes two front-to-back transmission gears, the number of connecting rods (433) corresponds to the number of transmission gears, the drive assembly includes a drive shaft (41) and two drive gears (431), and a linkage rod (439) is connected between the two drive gears (431) on the left and right sides; the corresponding drive gear (431) meshes with the two front-to-back transmission gears on the left or right side at the same time; the drive shaft (41) acts directly or indirectly on one of the drive gears (431), and an adjusting handwheel (411) is connected to the outer end of the drive shaft (41). By rotating the adjusting handwheel (411), multiple transmission gears rotate at a predetermined angle and stop at the corresponding position.

3. A roller changing mechanism with gap compensation function according to claim 2, characterized in that: A self-locking transmission component is provided between the drive shaft (41) and the corresponding drive gear (431). The self-locking transmission component is a worm gear transmission box (42). The drive shaft (41) is connected to the input end of the worm gear transmission box (42), and the corresponding drive gear (431) is connected to the output end of the worm gear transmission box (42). After the drive gear (431) rotates to the position, the worm gear transmission box (42) restricts the drive gear (431) from rotating in the opposite direction, so that the two transmission wheels (432) stop at the predetermined position.

4. A roller changing mechanism with gap compensation function according to claim 1, characterized in that: An eccentricity is formed between the center of the eccentric hole (4361) and the center of the shaft hole, and the size of the eccentricity is equal to 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 shaft hole is located directly above the center of the central hole (432b); when multiple transmission wheels (432) rotate 180 degrees synchronously, the center of the shaft hole moves to directly below the center of the central hole (432b).

5. A roller changing mechanism with gap compensation function according to claim 4, characterized in that: When the rotation angle of the transmission wheel (432) is greater than 180 degrees, the center of the shaft hole rotates around the center of the central hole (432b) and moves closer to the initial position, and drives the lifting component that has been extended downward to return to the starting position.

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