High-speed fin die cross-cutting mechanism

Abstract

This utility model relates to the field of fin mold technology and discloses a high-speed fin mold cross-cutting mechanism, including an upper cutter holder and a lower cutter holder. A cross-cutting sliding plate is provided on the upper cutter holder, and a power assembly is provided above the cross-cutting sliding plate. The power assembly includes a drive shaft arranged parallel to the cross-cutting sliding plate, with eccentric shafts at both ends of the drive shaft. A support base is provided on the upper cutter holder. The first end of the eccentric shaft is connected to the end of the drive shaft via a coupling, and a first bearing is mounted on the first end. A bearing support seat for fixing the first bearing is provided on the support base. A swing block is mounted on the second end of the eccentric shaft. Upper and lower striking blocks pass through the support base, with the lower ends of the upper and lower striking blocks abutting against the cross-cutting sliding plate, and the upper ends of the upper and lower striking blocks sleeved on the swing block. The above-mentioned high-speed fin mold cross-cutting mechanism has good stability, can be independently controlled, and will not generate recoil force on the mold, improving the overall stability and lifespan of the mold under high-speed conditions and reducing the defect rate of fins.

Description

Technical Field

[0001] This utility model relates to the field of fin mold technology, and in particular to a high-speed fin mold cross-cutting mechanism. Background Technology

[0002] Fin molds are key equipment in the production of core components for heat exchangers in air conditioning and refrigeration equipment. Their cross-cutting mechanism is responsible for precisely cutting continuously formed fin strips to a set length. Traditionally, the cross-cutting mechanism is integrated into the upper mold and is driven by the movement of the punch press slide. During operation, a cylinder pushes a guide rod to move, aligning the striking block with the upper mold's striking rod. When the punch press slide reaches the bottom dead center, the striking rod presses down on the striking block, driving the sliding plate to complete the cross-cutting cut. The return spring pulls the sliding plate back to its original position during the upper mold's return stroke.

[0003] However, as OEMs continue to increase their demand for production capacity, the fin stamping speed has increased from the traditional 200-250 times / minute to over 600 times / minute, with some high-end production lines even reaching 800 times / minute. This directly affects the stability and reliability of the cross-cutting mechanism, specifically as follows: the return spring generates a huge reverse impact force at the moment of release, which directly acts on the upper die, disrupting the overall dynamic balance of the die and causing the press to be unbalanced. This unbalanced load causes slight misalignment of the upper and lower cutters. Under high-speed conditions, the probability of abnormal wear of the cutting edge (commonly known as "blade chipping") increases significantly, and in severe cases, it can cause the cutting edge to break. In addition, the vibration caused by the impact force can also cause burrs and warping on the fin cut, and the product defect rate increases exponentially with the increase of speed. Utility Model Content

[0004] Based on the above, the purpose of this utility model is to provide a high-speed fin mold cross-cutting mechanism to achieve high-precision, high-stability, and high-speed fin production.

[0005] To achieve the above objectives, the present invention adopts the following technical solution:

[0006] A high-speed fin die cross-cutting mechanism includes an upper cutter holder and a lower cutter holder. The lower cutter holder has a lower cross-cutting cutter fixed below the fin's travel path. The upper cutter holder has a cross-cutting sliding plate that floats up and down above the fin's travel path. An upper cross-cutting cutter cooperating with the lower cross-cutting cutter is mounted on the sliding plate. A power assembly is located above the sliding plate. The power assembly includes a drive shaft arranged parallel to the sliding plate, with eccentric shafts at both ends. Supports are provided on the upper surface of the upper cutter holder corresponding to the positions of the eccentric shafts. The base has a first end of an eccentric shaft connected to the end of a transmission shaft via a coupling, and a first bearing is mounted on the first end. A bearing support seat for fixing the first bearing is provided on the support base. A swing block is mounted on the second end of the eccentric shaft, which is parallel to the first end but not on the same axis. An upper and lower striking block is passed through the support base. The lower end of the upper and lower striking block abuts against the transverse cutting sliding plate, and the upper end of the upper and lower striking block is sleeved on the swing block, so that the rotational motion of the swing block is converted into the lifting motion of the upper and lower striking block, thereby realizing the transverse cutting sliding plate driving the transverse cutting upper blade to move up and down.

[0007] As an alternative, the swing block is a rectangular block, which is rotatably connected to the second end of the eccentric shaft. The upper and lower blocks are provided with rectangular inner cavities, and the rectangular inner cavities have gaps that allow the swing block to move horizontally only.

[0008] As an alternative, a second bearing is provided at each of the four corners of the swing block. The outer circle of the second bearing extends beyond the edge of the swing block, and the second bearing makes rolling contact with the wall of the rectangular inner cavity.

[0009] As an alternative, a hole is made at the center of the swing block and a third bearing is provided between it and the eccentric shaft. A retaining ring is provided on the second end of the eccentric shaft to limit the third bearing.

[0010] As an alternative, the lower end of the upper and lower blocks extends into a rectangular portion that abuts against the transverse sliding plate. A guide block is provided on the support base, and a rectangular hole adapted to the rectangular portion is provided on the guide block. The guide block is used to limit the displacement of the upper and lower blocks.

[0011] As an alternative, a convex ring is provided on the eccentric shaft between the first end and the second end, one side of the first bearing abuts against the convex ring, and an anti-loosening lock ring is provided on the eccentric shaft abutting against the other side of the first bearing.

[0012] As an alternative, the power assembly also includes a drive motor and a reducer, with the drive shaft extending from both ends of the reducer. The reducer is mounted on the upper tool holder, and the drive motor is connected to the reducer.

[0013] As an alternative, the cross-cutting sliding plate is attached to the side surface of the upper tool holder, a fixing bolt extends from the side surface of the upper tool holder, the cross-cutting sliding plate is provided with a vertical waist-shaped hole for the fixing bolt to pass through, and the upper tool holder is provided with an ejector spring for supporting the cross-cutting sliding plate.

[0014] The beneficial effects of this utility model are:

[0015] This high-speed fin die cross-cutting mechanism does not rely on the movement of the punch press slide and can complete the cutting operation independently. It overcomes the problems of instantaneous backlash force generated on the upper die during the return stroke of conventional cross-cutting mechanisms due to the installation of high-load springs, which disrupts the dynamic balance of the die and causes problems such as punch press overload and blade wear. This high-speed fin die cross-cutting mechanism has good stability, can be controlled independently, and will not generate backlash force on the die, thereby improving the overall stability and life of the die under high-speed conditions and reducing the defect rate of fins. Attached Figure Description

[0016] Figure 1 This is a front view of the high-speed fin mold cross-cutting mechanism provided in this embodiment of the utility model;

[0017] Figure 2 This is a side view of the high-speed fin mold cross-cutting mechanism provided in this embodiment of the utility model;

[0018] Figure 3 This is a schematic diagram of the structure above the upper knife holder in the high-speed fin mold cross-cutting mechanism provided in this embodiment of the utility model.

[0019] In the attached image:

[0020] 1. Upper blade holder; 2. Lower blade holder; 3. Lower cross-cutting blade; 4. Cross-cutting sliding plate; 5. Upper cross-cutting blade; 6. Drive shaft; 7. Eccentric shaft; 8. Support base; 9. Coupling; 10. First bearing; 11. Bearing support seat; 12. Swing block; 13. Upper and lower blocks; 14. Rectangular inner cavity; 15. Second bearing; 16. Third bearing; 17. Snap ring; 18. Rectangular part; 19. Guide block; 20. Rectangular hole; 21. Convex ring; 22. Anti-loosening lock ring; 23. Drive motor; 24. Reducer; 25. Fixing bolt; 26. Vertical oblong hole. Detailed Implementation

[0021] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, the accompanying drawings show only the parts relevant to the present invention, not the entire structure.

[0022] In the description of this utility model, unless otherwise explicitly specified and limited, the terms "connected," "linked," and "fixed" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0023] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0024] In the description of this embodiment, terms such as "upper," "lower," "left," and "right" are based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of description and simplification of operation, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0025] Furthermore, the terms "first" and "second" are merely used to distinguish between different terms in description and do not have any special meaning.

[0026] Please see Figures 1 to 3As shown, this embodiment provides a high-speed fin mold cross-cutting mechanism, including an upper cutter holder 1 and a lower cutter holder 2. The lower cutter holder 2 is provided with a cross-cutting lower cutter 3 fixed below the fin's travel path. The upper cutter holder 1 is provided with a cross-cutting sliding plate 4 that floats up and down above the fin's travel path. The cross-cutting sliding plate 4 is provided with a cross-cutting upper cutter 5 that cooperates with the cross-cutting lower cutter 3. A power assembly is provided above the cross-cutting sliding plate 4. The power assembly includes a drive shaft 6 arranged parallel to the cross-cutting sliding plate 4. Eccentric shafts 7 are respectively provided at both ends of the drive shaft 6. A support base 8 is provided on the upper surface of the upper cutter holder 1 corresponding to the position of the eccentric shaft 7. The first end of the eccentric shaft 7 is connected to the end of the transmission shaft 6 through a coupling 9 and a first bearing 10 is mounted on the first end. A bearing support seat 11 for fixing the first bearing 10 is provided on the support base 8. A swing block 12 is mounted on the second end of the eccentric shaft 7, which is parallel to the first end but not on the same axis. An upper and lower block 13 is passed through the support base 8. The lower end of the upper and lower block 13 abuts against the transverse cutting sliding plate 4, and the upper end of the upper and lower block 13 is sleeved on the swing block 12, so that the rotational motion of the swing block 12 is converted into the lifting motion of the upper and lower block 13, thereby realizing the transverse cutting sliding plate 4 driving the transverse cutting upper blade 5 to move up and down.

[0027] Thus, by combining the swing block 12 with the upper and lower striking blocks 13, the power of the drive shaft 6 is transmitted to the cross-cutting sliding plate 4, thereby controlling the cross-cutting upper blade 5 to move up and down in a regular manner, and cooperating with the cross-cutting lower blade 3 to complete the fin cutting operation; this structure is stable, has high motion accuracy, and the cross-cutting sliding plate 4 and the cross-cutting upper blade 5 move vertically at high speed, which can meet the requirements of high-speed operation.

[0028] In order to achieve precise linkage and stable power transmission between the swing block 12 and the upper and lower striking blocks 13, the swing block 12 in this embodiment is set as a rectangular block. The swing block 12 is rotatably connected to the second end of the eccentric shaft 7. The upper and lower striking blocks 13 are provided with a rectangular inner cavity 14, and a gap is left in the rectangular inner cavity 14 that only allows the swing block 12 to move horizontally.

[0029] Thus, the eccentric shaft 7 drives the swing block 12 to perform circular motion. The rectangular inner cavity 14 constrains the circular motion of the swing block 12 into a motion that is "free in the horizontal direction and rigid in the vertical direction." That is, when the eccentric shaft 7 rotates, the swing block 12 at the second end is limited by the rectangular inner cavity 14 and can only maintain its posture by moving up and down and left and right. When the swing block 12 moves left and right, the rectangular inner cavity 14 compensates for the relative displacement. Therefore, the upper and lower block 13 can only move up and down driven by the swing block 12 and will not sway left and right. The rectangular fit is more wear-resistant than the cam fit and can withstand greater lateral torque, resulting in more stable power transmission.

[0030] Furthermore, a second bearing 15 is provided at each of the four corners of the swing block 12. The outer circle of the second bearing 15 extends beyond the edge of the swing block 12, and the second bearing 15 rolls into contact with the wall of the rectangular inner cavity 14.

[0031] Therefore, by replacing the swing block 12 with the second bearing 15 to form rolling contact with the upper and lower blocks 13, wear and energy consumption are reduced. In particular, the service life can be extended during high-frequency swinging, and problems such as motion jamming and inaccurate movement caused by local wear can be avoided.

[0032] Furthermore, a hole is opened at the center of the swing block 12 and a third bearing 16 is provided between it and the eccentric shaft 7. A retaining ring 17 is provided on the second end of the eccentric shaft 7 to limit the third bearing 16.

[0033] Therefore, the connection position between the swing block 12 and the eccentric shaft 7 is centrally arranged to ensure that the centrifugal force of the eccentric shaft 7 is symmetrical, reduce the additional torque, and reduce the vibration of the swing block 12; the third bearing 16 bears the radial force and optimizes the load of the eccentric shaft 7; the snap ring 17 prevents the third bearing 16 from moving axially, ensuring the relative position of the eccentric shaft 7 and the swing block 12 is stable and avoiding dislocation caused by vibration.

[0034] Optionally, the lower end of the upper and lower striking blocks 13 extends into a rectangular portion 18 that abuts against the transverse sliding plate 4. A guide block 19 is provided on the support base 8. A rectangular hole 20 adapted to the rectangular portion 18 is provided on the guide block 19. The guide block 19 is used to limit the displacement of the upper and lower striking blocks 13.

[0035] Among them, the lower end of the upper and lower punching blocks 13 can form a certain limiting and guiding effect when passing through the support base 8. In order to further improve the repeatability accuracy of the upper and lower punching blocks 13, a guide block 19 is added. Moreover, the cooperation between the rectangular part 18 and the rectangular hole 20 has strong anti-eccentric load capacity and is more suitable for high-speed punching.

[0036] Optionally, a convex ring 21 is provided on the eccentric shaft 7 between the first end and the second end, one side of the first bearing 10 abuts against the convex ring 21, and an anti-loosening locking ring 22 is provided on the eccentric shaft 7 abutting against the other side of the first bearing 10.

[0037] Thus, the convex ring 21 and the anti-loosening locking ring 22 are located on both sides of the first bearing 10, and work together to lock the first bearing 10 on the eccentric shaft 7, eliminating axial clearance, preventing the first bearing 10 from wearing due to fretting caused by bidirectional load, and improving structural stability.

[0038] Optionally, the power assembly also includes a drive motor 23 and a reducer 24, with the transmission shaft 6 extending from both ends of the reducer 24. The reducer 24 is mounted on the upper tool holder 1, and the drive motor 23 is connected to the reducer 24.

[0039] Therefore, by directly fixing the reducer 24 to the upper tool holder 1, and integrating the drive motor 23 with the reducer 24, the power component and the upper tool holder 1 are integrated into one, achieving independent drive, and reducing the coupling 9 and intermediate transition parts, thus improving the motion accuracy; in addition, the output shafts at both ends make the load of the eccentric shaft 7 symmetrical, avoiding the bending of the transmission shaft 6 caused by unilateral force, and realizing the synchronous drive of the transverse cutting sliding plate 4 at both ends.

[0040] Optionally, the cross-cutting sliding plate 4 is attached to the side surface of the upper cutter holder 1, a fixing bolt 25 extends from the side surface of the upper cutter holder 1, the cross-cutting sliding plate 4 is provided with a vertical waist-shaped hole 26 for the fixing bolt 25 to pass through, and the upper cutter holder 1 is provided with an ejector spring for supporting the cross-cutting sliding plate 4.

[0041] This allows the transverse cutting sliding plate 4 to float up and down only along the upper blade holder 1, further ensuring the movement accuracy of the transverse cutting upper blade 5; the ejector spring is used to help the transverse cutting sliding plate 4 move upward and reset, and under normal conditions, to create a gap between the transverse cutting upper blade 5 and the transverse cutting lower blade 3 for the fins to pass through.

[0042] During operation, the drive motor 23 and the reducer 24 work together to drive the transmission shaft 6 to rotate, which in turn drives the eccentric shafts 7 at both ends to rotate. This, in turn, drives the upper and lower striking blocks 13 to move vertically through the swing block 12. As a result, the upper and lower striking blocks 13 create downward pressure, driving the upper cross-cutting blade 5 on the cross-cutting sliding plate 4 to move downward against the force of the ejector spring. This blade works in conjunction with the fixed lower cross-cutting blade 3 to complete the precise cutting of the fins. After the cutting action is completed, the upper and lower striking blocks 13 immediately cease to exert downward pressure on the cross-cutting sliding plate 4. Under the action of the ejector spring, the upper cross-cutting blade 5 quickly returns to its original position, allowing the fins to pass through the gap and advance one step before proceeding to the next cross-cut.

[0043] In summary, this high-speed fin die cross-cutting mechanism does not rely on the movement of the punch press slide. It can independently drive the upper cross-cutting blade 5 to complete the cutting operation, overcoming the problems of punch press overload, blade chipping, and burrs caused by the instantaneous backlash force generated on the upper die during the return stroke of the high-load spring in conventional cross-cutting mechanisms. This is because such a mechanism disrupts the dynamic balance of the die and causes problems such as punch press overload, blade chipping, and burrs. This high-speed fin die cross-cutting mechanism has good stability and strong controllability, and does not generate backlash force on the die. It improves the overall stability and lifespan of the die under high-speed conditions, reduces the defect rate of fins, and meets the requirements of high-speed fin processing.

[0044] Obviously, the above embodiments of this utility model are merely examples for clearly illustrating the present utility model, and are not intended to limit the implementation of the present utility model. Those skilled in the art can make various obvious changes, readjustments, and substitutions without departing from the protection scope of this utility model. It is neither necessary nor possible to exhaustively describe all embodiments here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this utility model should be included within the protection scope of the claims of this utility model.

Claims

1. A high-speed fin mold cross-cutting mechanism, comprising an upper cutter holder (1) and a lower cutter holder (2), wherein the lower cutter holder (2) is provided with a cross-cutting lower cutter (3) fixed below the fin travel path, and the upper cutter holder (1) is provided with a cross-cutting sliding plate (4) that floats up and down above the fin travel path, and the cross-cutting sliding plate (4) is provided with a cross-cutting upper cutter (5) that cooperates with the cross-cutting lower cutter (3), characterized in that, A power assembly is provided above the transverse cutting sliding plate (4). The power assembly includes a drive shaft (6) arranged parallel to the transverse cutting sliding plate (4). Eccentric shafts (7) are respectively provided at both ends of the drive shaft (6). A support base (8) is provided on the upper surface of the upper tool holder (1) corresponding to the position of the eccentric shaft (7). The first end of the eccentric shaft (7) is connected to the end of the drive shaft (6) through a coupling (9), and a first bearing (10) is mounted on the first end. The support base (8) is provided with a fixture to fix the first bearing (10). The bearing support seat (11) is provided with a swing block (12) mounted on the second end of the eccentric shaft (7) which is parallel to the first end but not on the same axis. The support base (8) is provided with an upper and lower block (13). The lower end of the upper and lower block (13) abuts against the transverse cutting sliding plate (4). The upper end of the upper and lower block (13) is sleeved on the swing block (12), so that the rotational motion of the swing block (12) is converted into the lifting motion of the upper and lower block (13), thereby realizing that the transverse cutting sliding plate (4) drives the transverse cutting upper blade (5) to move up and down.

2. The high-speed fin mold cross-cutting mechanism according to claim 1, characterized in that, The swing block (12) is a rectangular block. The swing block (12) is rotatably connected to the second end of the eccentric shaft (7). The upper and lower blocks (13) have a rectangular inner cavity (14) with a gap in the rectangular inner cavity (14) that allows the swing block (12) to move horizontally only.

3. The high-speed fin mold cross-cutting mechanism according to claim 2, characterized in that, The four corners of the swing block (12) are respectively provided with second bearings (15), the outer circle of the second bearings (15) extends beyond the edge of the swing block (12), and the second bearings (15) roll in contact with the wall of the rectangular inner cavity (14).

4. The high-speed fin mold cross-cutting mechanism according to claim 3, characterized in that, The swing block (12) has an opening at its center and a third bearing (16) is provided between it and the eccentric shaft (7). A retaining ring (17) is provided on the second end of the eccentric shaft (7) to limit the third bearing (16).

5. The high-speed fin mold cross-cutting mechanism according to claim 1, characterized in that, The lower end of the upper and lower striking blocks (13) extends into a rectangular portion (18) that abuts against the transverse sliding plate (4). A guide block (19) is provided on the support base (8). A rectangular hole (20) adapted to the rectangular portion (18) is provided on the guide block (19). The guide block (19) is used to limit the displacement of the upper and lower striking blocks (13).

6. The high-speed fin mold cross-cutting mechanism according to claim 1, characterized in that, A convex ring (21) is provided on the eccentric shaft (7) between the first end and the second end. One side of the first bearing (10) abuts against the convex ring (21). An anti-loosening lock ring (22) is provided on the eccentric shaft (7) abutting against the other side of the first bearing (10).

7. The high-speed fin mold cross-cutting mechanism according to claim 1, characterized in that, The power assembly also includes a drive motor (23) and a reducer (24). The transmission shaft (6) extends out of both ends of the reducer (24). The reducer (24) is mounted on the upper tool holder (1). The drive motor (23) is connected to the reducer (24).

8. The high-speed fin mold cross-cutting mechanism according to claim 1, characterized in that, The transverse cutting sliding plate (4) is attached to the side surface of the upper knife holder (1). A fixing bolt (25) extends out from the side surface of the upper knife holder (1). The transverse cutting sliding plate (4) is provided with a vertical waist-shaped hole (26) for the fixing bolt (25) to pass through. The upper knife holder (1) is provided with an ejector spring for supporting the transverse cutting sliding plate (4).

Images