Pair of rollers centering adjusting mechanism applied to square tube roll forming system

Abstract

The utility model relates to a pair of compression roller centering adjusting mechanism applied to square tube roll forming system, adopts box base and end cover positioning worm wheel, and connects base on support and worm wheel speed reducer's casing simultaneously, makes the structure of base more stable, the pressure of worm wheel is distributed on both sides' support positioning part, the support positioning part of both sides of worm wheel is supported by the matching hole and the inner circumferential wall of recess respectively, eliminates the worm wheel twist tendency, makes the annular end face of both ends of worm wheel respectively with base inner wall and end cover complete adhesion, reduces the local pressure between worm wheel and base inner wall, end cover, reduces the wear degree when worm wheel rotates relative to base inner wall or end cover, can eliminate wear when the hardness and lubricity of annular end face of both ends of worm wheel, base inner wall and end cover end face meet certain conditions, thereby prolongs the service life of worm wheel and positioning sleeve, long-term keeps worm wheel high-precision transmission.

Description

Technical Field

[0001] This utility model belongs to the technical field of square tube rolling forming equipment, specifically relating to a pair of pressure roller centering adjustment mechanism applied to a square tube rolling forming system. Background Technology

[0002] In square tube roll forming equipment, paired pressure rollers gradually bend steel strips by extruding them, ultimately forming square tubes, such as the multi-specification square tube roll forming system disclosed in Chinese Patent CN113649432B. When using steel strips of different thicknesses to roll tubes, if the spacing between the paired pressure rollers is not adjusted, the outer diameter of the finished square tube will increase. To overcome this problem, a fine-tuning mechanism for the spacing between the paired pressure rollers is required. A conventional fine-tuning mechanism for the spacing between the paired pressure rollers, as described in the aforementioned prior art "multi-specification square tube roll forming system," involves axially sliding the bearing housing of the pressure roller shaft onto a support. A worm gear is threaded onto the distal end of the bearing housing of one pressure roller shaft. A worm gear reducer is then used to drive the worm gear to rotate, causing the bearing housing to slide axially, thereby adjusting the spacing between the paired pressure rollers. This structure requires axial positioning of the worm gear, while the conventional positioning method is to press one end of the worm gear onto the support, such as... Figure 1 As shown, during the worm gear and worm drive process, one side of the worm gear is continuously subjected to pressure from the worm. Combined with the influence of the bearing housing assembly clearance, this causes the end of the worm gear away from the pressing component to tend to tilt downwards. As a result, when the worm gear drives the two bearing housings to move towards each other, the worm gear is subjected to a reaction force. The pressure between the lower part of the worm gear and the pressing component is greater than the pressure on the lower part of the pressing component. Conversely, the pressure between the lower part of the worm gear and the support is greater than the pressure between the upper part of the worm gear and the support. This unbalanced pressure causes severe wear on the upper part of the pressing component, severe wear on the surface of the lower part of the support that contacts the worm gear, and wear on both sides of the part of the worm gear that is pressed. This leads to increased axial movement of the worm gear, affecting its service life and transmission accuracy. Utility Model Content

[0003] The technical problem to be solved by this utility model is to provide a pair of pressure roller centering adjustment mechanism for a square tube rolling forming system, which solves the technical problem that the unreasonable worm gear positioning structure in the mechanism causes the pressing parts and worm gear to be easily worn locally, affecting the service life of the worm gear and pressing parts.

[0004] To solve the above-mentioned technical problems, the technical solution adopted by this utility model is as follows: a pair of pressure roller centering adjustment mechanism applied to a square tube roll forming system, comprising two opposing supports, each of which is connected to a bearing seat. The two bearing seats are coaxially arranged, and each bearing seat is rotatably connected to a rotating shaft via a bearing. The opposing ends of the two rotating shafts extend out of the bearing seats and are respectively connected to pressure rollers. The opposing ends of the two rotating shafts are also connected by a main drive shaft. At least one end of the main drive shaft is coaxial with and axially slidably inserted into one of the rotating shafts. The main drive shaft is circumferentially fixedly connected to the two rotating shafts, and one rotating shaft is located away from the pressure roller. One end extends out of the bearing housing for connecting to the drive device. The two bearing housings are axially sliding and circumferentially fixedly connected to corresponding brackets. The disjoint ends of the two bearing housings extend out of the corresponding brackets and are respectively provided with external threads on their outer circumferential walls. A worm gear is connected to each of the two bearing housings in a corresponding manner. Any worm gear is sleeved on the external thread of the corresponding bearing housing and threadedly connected to the external thread. A worm gear reducer is also connected to each of the two brackets in a corresponding manner. The input shafts of the two worm gear reducers are coaxially arranged and connected by a secondary drive shaft. At least one end of the secondary drive shaft is coaxial with the input shaft of one of the worm gear reducers. Furthermore, the components are axially slidably connected, with the input shaft of one worm gear reducer connected to the drive motor. The output shafts of the two worm gear reducers are respectively connected to worms meshing with corresponding worm wheels. Any worm wheel is axially fixed to an adjacent support via a positioning sleeve, and the worm wheel is rotatably connected to the positioning sleeve. The positioning sleeve includes a box-shaped base fixedly connected to the outside of the support and an end cap. The base has a through hole for a bearing seat to pass through and a mating hole coaxially connected to the through hole with an inner diameter larger than the through hole. The mating hole is used to engage the worm wheel. Both ends of the worm wheel extend axially outwards to form supporting positioning portions. The outer diameter of the support positioning part is smaller than the outer diameter of the worm gear. The mating hole is a stepped hole. The end of the mating hole close to the through hole is adapted to one support positioning part, and the end of the mating hole away from the through hole is clearance-fitted with the worm gear. The end cover is provided with a groove adapted to another support positioning part. The end cover is closed on the end of the base away from the bracket. The other support positioning part is embedded in the groove. The side wall of the base near the worm gear reducer is also provided with a through hole for the worm to pass through. The worm passes through the through hole and extends into the base to mesh with the worm gear. The side wall of the base with the through hole is fixedly connected to the housing of the worm gear reducer.

[0005] As a preferred embodiment, the base has a cleaning hole at its bottom that faces the worm gear.

[0006] As a preferred embodiment, the bracket is provided with a sliding hole that mates with a corresponding bearing seat. The bearing seat is slidably inserted into the sliding hole. An axially extending groove is provided on the inner wall of the sliding hole. A slider is provided on the bearing seat that is inserted into the groove. The slider and the groove are slidably engaged. The bearing seat slides back and forth along the groove under the guidance of the slider.

[0007] As a preferred embodiment, the end of the base connected to the bracket is provided with a protruding ring that can be inserted into a sliding hole. When the base and the bracket are tightly fitted together, the protruding ring is inserted into the sliding hole, and the protruding ring and the sliding hole are tightly fitted together.

[0008] The beneficial effects of this utility model are as follows: This utility model uses a box-type base and end caps to position the worm gear, and connects the base to both the bracket and the housing of the worm gear reducer, making the base structure more stable. The pressure on the worm gear is distributed to the support positioning parts on both sides. The support positioning parts on both sides of the worm gear are supported by the inner circumferential walls of the mating holes and grooves, respectively, eliminating the tendency of the worm gear to twist. This allows the annular end faces at both ends of the worm gear to fully fit with the inner wall of the base and the end cap, respectively, reducing the local pressure between the worm gear and the inner wall of the base and the end cap, and reducing the degree of wear when the worm gear rotates relative to the inner wall of the base or the end cap. When the hardness and lubrication of the annular end faces at both ends of the worm gear, the inner wall of the base, and the end cap end faces meet certain conditions, wear can be eliminated, thereby extending the service life of the worm gear and the positioning sleeve, and maintaining high-precision transmission of the worm gear for a long time. Attached Figure Description

[0009] The specific embodiments of this utility model will be further described in detail below with reference to the accompanying drawings, wherein: Figure 1 This is a schematic diagram of a conventional pair of pressure roller centering and adjusting mechanism; Figure 2 This is a schematic diagram of the structure of the paired pressure roller centering adjustment mechanism described in this utility model; Figure 3 This is an exploded view of the specific connection structure between the positioning sleeve and the worm gear described in this utility model; Figures 1-3 In the middle: 1. Bracket; 2. Bearing housing; 3. Bearing; 4. Rotating shaft; 5. Pressure roller; 6. Main drive shaft; 7. Convex ring; 8. Worm gear; 9. Worm gear reducer; 10. Secondary drive shaft; 11. Drive motor; 12. Worm; 13. Positioning sleeve; 1301. Base; 1302. End cover; 14. Slide groove; 15. Slider; 16. Through hole; 17. Mating hole; 18. Support positioning part; 19. Groove; 20. Through hole; 21. Cleaning hole; 22. Sliding hole; 23. Stepped surface. Detailed Implementation

[0010] The specific implementation scheme of this utility model will now be described in detail with reference to the accompanying drawings.

[0011] like Figure 2 and Figure 3The paired pressure roller centering adjustment mechanism shown in the square tube roll forming system includes two opposing supports 1, each with a bearing seat 2 connected to it. The two bearing seats 2 are coaxially arranged, and each bearing seat 2 has a rotating shaft 4 rotatably connected to it via a bearing 3. The opposing ends of the two rotating shafts 4 extend out of the bearing seats 2 and are respectively connected to pressure rollers 5. The opposing ends of the two rotating shafts 4 are also connected to each other via a main drive shaft 6 to achieve synchronous rotation. At least one end of the main drive shaft 6 is coaxial with one of the rotating shafts 4 and axially slides into it to allow the two rotating shafts 4 to move towards or away from each other. The main drive shaft 6 is circumferentially fixed to the two rotating shafts 4, and an axial sliding connection between the main drive shaft 6 and the rotating shafts 4 can be achieved using a spline connection structure. Figure 2 As shown, one end of a rotating shaft 4 on the right side, away from the pressure roller 5, extends out of the bearing seat 2 to connect to the drive device. The two bearing seats 2 are axially sliding and circumferentially fixedly connected to the corresponding brackets 1. The opposite ends of the two bearing seats 2 extend out of the corresponding brackets 1 and are respectively provided with external threads on their outer circumferential walls. A worm gear 8 is connected to each of the two bearing seats 2 in a corresponding manner. Any worm gear 8 is sleeved on the external thread of the corresponding bearing seat 2 and threadedly connected to the external thread. A worm gear reducer 9 is also connected to each of the two brackets 1 in a corresponding manner. The input shafts of the two worm gear reducers 9 are coaxially arranged and are connected by a secondary drive shaft 10 to achieve synchronization of the two worm gear reducers 9. At least one end of the secondary drive shaft 10 is coaxial with and axially slidingly inserted into the input shaft of one of the worm gear reducers 9. The input shaft of one of the worm gear reducers 9 is connected to the drive motor 11, and the drive motor 11 drives the two worm gear reducers 9 to rotate synchronously.

[0012] Two worm gear reducers 9 have worms 12 connected to their respective output shafts, each meshing with a corresponding worm wheel 8. Each worm wheel 8 is axially fixed to an adjacent support 1 via a positioning sleeve 13. The worm wheel 8 is rotatably connected to the positioning sleeve 13, allowing it to rotate in a fixed position to drive the threaded bearing seat 2 to move axially. The positioning sleeve 13 includes a box-shaped base 1301 fixedly connected to the outside of the support 1 and an end cap 1302. The base 1301 has a through hole 16 for the bearing seat 2 to pass through and a mating hole 17 coaxially connected to the through hole 16 with an inner diameter larger than the through hole 16. The mating hole 17 is used to engage the worm wheel 8. Both ends of the worm wheel 8 extend axially outwards into annular support and positioning portions 18, the outer diameter of which is smaller than the outer diameter of the worm wheel 8. The mating hole 17 is a stepped hole, with one end of the mating hole 17 approaching the through hole 16 and... Figure 3 A support and positioning part 18 on the right side of the worm gear 8 is adapted to fit the end of the mating hole 17 away from the through hole 16 and has a clearance fit with the worm gear 8. The end cover 1302 is provided with a corresponding... Figure 3The groove 19 is adapted to a support and positioning part 18 on the left side of the worm gear 8. The end cap 1302 covers the end of the base 1301 away from the bracket 1. The other support and positioning part 18 is embedded in the groove 19. A through hole 20 is also provided on the side wall of the base 1301 near the worm gear reducer 9 for the worm 12 to pass through. The worm 12 passes through the through hole 20 and extends into the base 1301 to mesh with the worm gear 8. The side wall of the base 1301 with the through hole 20 is fixedly connected to the housing of the worm gear reducer 9.

[0013] The sidewall of the worm gear 8 located outside the right-side support and positioning part 18 is in contact with the stepped surface 23 of the mating hole 17, and the sidewall of the worm gear 8 located outside the left-side support and positioning part 18 is in contact with the right end face of the end cap 1302. When the worm gear 8 rotates, its two sides are supported by the entire stepped surface 23 and the right end face of the end cap 1302, thus maintaining the axial position of the worm gear 8. Since the pressure of the worm 12 on the worm gear 8 is between the stepped surface 23 and the right end face of the end cap 1302, and the support and positioning parts 18 on both sides of the worm gear 8 are supported by the mating hole 17 and the groove 19, the tendency to tilt is eliminated, and the reaction force on the worm gear 8 during rotation is evenly applied to the stepped surface 23 and the right end face of the end cap 1302. This avoids the problem of excessive local stress on the stepped surface 23 and the right end face of the end cap 1302, which leads to severe local wear.

[0014] In this embodiment, a cleaning hole 21 is provided at the bottom of the base 1301, which is directly opposite to the worm gear 8. Its function is to facilitate cleaning of the worm gear 8, worm 12, step surface 23 and right end face of end cap 1302.

[0015] The bracket 1 has a sliding hole 22 that mates with the corresponding bearing seat 2. The bearing seat 2 is slidably inserted into the sliding hole 22. An axially extending groove 14 is provided on the inner wall of the sliding hole 22. A slider 15 is provided on the bearing seat 2 and inserted into the groove 14. The slider 15 and the groove 15 are slidably engaged. Under the guidance of the slider 15, the bearing seat 2 slides back and forth along the groove 14.

[0016] like Figure 3 As shown, the base 1301 is provided with a protruding ring 7 that can be inserted into the sliding hole 22 at one end connected to the bracket 1. When the base 1301 and the bracket 1 are tightly fitted together, the protruding ring 7 is inserted into the sliding hole 22 and the protruding ring 7 is tightly fitted with the sliding hole 22.

[0017] The tight fit between the convex ring 7 and the sliding hole 22 improves the connection stability and reliability between the positioning sleeve 13 and the bracket 1, while also improving the coaxiality of the mating hole 17 and through hole 16 in the positioning sleeve 13 with the bearing seat 2, making the fit between the positioning sleeve 13 and the worm gear 8 more precise.

[0018] The working process of this utility model is as follows: Figure 2As shown, when rolling strips of different thicknesses, the drive motor 11 drives two worm gear reducers 9 to rotate synchronously. The two worm gear reducers 9 drive worm wheels 8 to rotate synchronously through worms 12. The rotation of the two worm wheels 8 drives two bearing seats 2 to move equidistantly towards or away from each other. When the two bearing seats 2 move, their centers remain unchanged.

[0019] The above embodiments are merely illustrative of the principles and effects of the present invention, as well as some examples of its application, and are not intended to limit the present invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the inventive concept of the present invention, and these modifications and improvements are all within the scope of protection of the present invention.

Claims

1. A pair of pressure roller centering adjustment mechanism applied to a square tube roll forming system, comprising two opposing supports (1), each of the two supports (1) being connected to a bearing seat (2), the two bearing seats (2) being coaxially arranged, and rotating shafts (4) being rotatably connected to each of the two bearing seats (2) via bearings (3), the opposing ends of the two rotating shafts (4) extending out of the bearing seats (2) and respectively connected to pressure rollers (5), the opposing ends of the two rotating shafts (4) being connected to each other via a main drive shaft (6), at least one end of the main drive shaft (6) being coaxial with and axially slidingly inserted into one of the rotating shafts (4), the main drive shaft (6) being circumferentially fixedly connected to the two rotating shafts (4), and the end of one rotating shaft (4) away from the pressure roller (5) extending out of the bearing seat (2) for connecting a drive device, characterized in that, The two bearing seats (2) are axially sliding and circumferentially fixedly connected to the corresponding brackets (1). The disjoint ends of the two bearing seats (2) extend out of the corresponding brackets (1) and are respectively provided with external threads on their outer circumferential walls. A worm gear (8) is connected to each of the two bearing seats (2) in a corresponding manner. Any worm gear (8) is sleeved on the external thread of the corresponding bearing seat (2) and threadedly connected to the external thread. A worm gear reducer (9) is also connected to each of the two brackets (1) in a corresponding manner. The input shafts of the two worm gear reducers (9) are coaxially arranged and connected by a secondary drive shaft (10). At least one end of the secondary drive shaft (10) is connected to the... The input shafts of one worm gear reducer (9) are coaxial and axially slidably connected. The input shaft of one worm gear reducer (9) is connected to the drive motor (11). The output shafts of the two worm gear reducers (9) are respectively connected to worms (12) that mesh with the corresponding worm wheels (8). Any worm wheel (8) is axially fixed to the adjacent bracket (1) through a positioning sleeve (13). The worm wheel (8) is rotatably connected to the positioning sleeve (13). The positioning sleeve (13) includes a box-shaped base (1301) fixedly connected to the outside of the bracket (1) and an end cap (1302). The base (1301) has a hole for... The bearing housing (2) has a through hole (16) through which it passes and a mating hole (17) that is coaxially connected to the through hole (16) and has an inner diameter larger than the through hole (16). The mating hole (17) is used to engage the worm gear (8). Both ends of the worm gear (8) extend axially outward to form support and positioning parts (18). The outer diameter of the support and positioning parts (18) is smaller than the outer diameter of the worm gear (8). The mating hole (17) is a stepped hole. One end of the mating hole (17) close to the through hole (16) is fitted with a support and positioning part (18), and the other end of the mating hole (17) away from the through hole (16) is clearance-fitted with the worm gear (8). The end cap (1302) The base (1301) is provided with a groove (19) that is adapted to another support positioning part (18). The end cap (1302) is covered on the end of the base (1301) away from the bracket (1). The other support positioning part (18) is embedded in the groove (19). The side wall of the base (1301) near the worm gear reducer (9) is also provided with a through hole (20) for the worm (12) to pass through. The worm (12) passes through the through hole (20) and extends into the base (1301) to mesh with the worm wheel (8). The side wall of the base (1301) with the through hole (20) is fixedly connected to the housing of the worm gear reducer (9).

2. The paired pressure roller centering adjustment mechanism according to claim 1, characterized in that, The base (1301) has a cleaning hole (21) at the bottom that is directly opposite the worm gear (8).

3. The paired pressure roller centering adjustment mechanism according to claim 1 or 2, characterized in that, The bracket (1) has a sliding hole (22) that mates with the corresponding bearing seat (2). The bearing seat (2) is slidably inserted into the sliding hole (22). An axially extending groove (14) is provided on the inner wall of the sliding hole (22). A slider (15) is provided on the bearing seat (2) and inserted into the groove (14). The slider (15) and the groove (14) are slidably engaged. The bearing seat (2) slides back and forth along the groove (14) under the guidance of the slider (15).

4. The paired pressure roller centering adjustment mechanism according to claim 3, characterized in that, The base (1301) is connected to the bracket (1) at one end with a protruding ring (7) that can be inserted into the sliding hole (22). When the base (1301) and the bracket (1) are in close contact, the protruding ring (7) is inserted into the sliding hole (22) and the protruding ring (7) is in close contact with the sliding hole (22).

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