A fin press

Abstract

The application discloses a fin press forming machine, which comprises a rack body, an upper machine shell, an upper sliding table, an upper and lower die connecting rod, a shaping table, a feeding rocker, a lower sliding table, a cam device and a horizontal sliding table. The cam device is connected with the upper and lower die connecting rod through a fork straight handle lever mechanism and connected with the feeding rocker through a fork corner lever mechanism. First and second cams are further arranged for being connected with the first and second fork heads respectively. In the first and second cams, at least the first cam is configured to satisfy a selected curve stroke to form a cam profile line of the first cam. The fork straight handle lever mechanism and the fork corner lever mechanism are particularly added. The first cam starts with zero speed and zero acceleration and stops with zero speed and zero acceleration, so that there is no longer movement impact, impact force between structural members is avoided, impact noise is avoided, and movement energy loss is reduced.

Description

Technical Field

[0001] This invention relates to the field of fin forming and processing technology in plate-fin heat exchangers, and particularly to a fin forming machine. Background Technology

[0002] Plate-fin heat exchangers are characterized by high heat exchange efficiency, small size, and light weight. Currently, they are widely used in the construction machinery, general machinery, and internal combustion locomotive industries for heating and / or cooling various oils, waters, and gases. For example, aluminum plate-fin heat exchangers are widely used in air separation equipment; in petrochemical plants such as ethylene plants, synthetic ammonia plants, and natural gas liquefaction (LNG) and separation units; in cryogenic hydrogen, helium, refrigeration, and liquefaction equipment; in the refrigeration and air conditioning fields; and in the automotive and aerospace industries.

[0003] In aluminum plate-fin heat exchanger structures, fins are the heat exchange elements. The general structural form of fin 900 is shown in the attached figure. Figure 1 As shown, in aluminum plate-fin heat exchanger structures, aluminum-magnesium alloy foil is commonly used as the fin material, and it is currently widely formed using a fin punching press. The traditional punching press structure and its components are shown in the appendix. Figure 2 Appendix Figure 3 Specifically, it includes components such as frame body 1, upper housing 2, upper slide 3, upper die connecting rod 4, forming table 5, feed rocker 6, lower slide 7, rocker arm 8, electrical control box 9, spindle box 10, cam device 11, gearbox 12, electric motor 13, oil pump device 14, clutch 15, lubricating oil distributor 16, and horizontal slide 19. The electric motor 13 outputs power, which is converted and transmitted to the spindle box 10 via the gearbox 12. The spindle box 10 drives the cam device 11 to rotate. The two sets of eccentric cams on the cam device 11 drive the upper and lower slide 7 to move up and down through the upper die connecting rod 4, and drive the horizontal slide 19 to move horizontally through the feed rocker 6. In the traditional fin punch press structure, a return spring needs to be set so that the return of the upper and lower slides after the cam device wobbles is controlled by the spring force and the system elastic force-mass inertia.

[0004] In the process of realizing this invention, the inventors discovered that, due to the structure of traditional punch presses, traditional punch presses have at least the following problems: 1. The upper and lower slides of the punch press have a fixed stroke, while the height of the punched fins is always less than the slide stroke. As a result, during the punching process, there is a collision between the mold fixed on the slide and the workpiece. 2. The horizontal movement stroke and amplitude of the horizontal slide are adjusted and limited by mechanical impact limit blocks, which inevitably causes mechanical impact noise and mechanical impact force between structural components; 3. The stripper plate moves with the mold in the first half of its stroke. It stops moving after contacting the guide fin plate (height limit plate). This stopping moment is also a collision process. 4. The cam profile of the upper and lower sliders is unreasonable, which prevents the upper and lower sliders from starting and stopping at zero speed and zero acceleration during reciprocating motion. This results in unstable motion / collision of the upper and lower sliders.

[0005] 5. During the reciprocating motion of the upper and lower sliders, the spring force is used to reset them. However, the spring force is limited and the slider mass is large, which causes the acceleration generated by the slider under the action of the spring force to be much smaller than the acceleration corresponding to the cam profile at a certain phase point. As a result, inertial motion distortion and rear-end collision occur, and an impact occurs at the moment of rear-end collision.

[0006] In each of the above-described impact processes, some kinetic energy is generated into noise, and even more kinetic energy is converted into heat and lost. Therefore, how to solve the above problems becomes the subject of this invention. Summary of the Invention

[0007] The purpose of this invention is to provide a fin forming machine for stamping fins in plate-fin heat exchangers, which solves the problems of traditional punch presses where some kinetic energy is generated into noise during each impact process and more kinetic energy is converted into heat and lost. At the same time, the movement range of the upper and lower slides and the horizontal slide can be adjusted according to actual needs.

[0008] To achieve the above objectives, this invention proposes a fin forming machine for stamping fins in plate-fin heat exchangers. The forming machine includes a frame, an upper housing, an upper slide, upper and lower die connecting rods, a forming table, a feed rocker arm, a lower slide, a cam device, and a horizontal slide. The cam device is connected to either the upper or lower slide via the upper and lower die connecting rods, and is connected to the horizontal slide via the feed rocker arm. Its innovation lies in: The cam device is connected to the upper and lower die connecting rods via a fork-head straight handle lever mechanism. The fork-head straight handle lever mechanism includes a fork-head straight handle lever, a first lead screw, a first slider, a first motion transmission shaft, a first gear pair, a first shaft, and a first support. The fork-head straight handle lever includes a first fork head and a straight handle portion. One end of the straight handle portion is integral with the first fork head, and the other end is hinged to the first support via the first shaft. A first sliding groove is provided on the straight handle portion along its length. The first slider is installed in the first sliding groove and connected to the first lead screw thread pair, allowing it to move along the first sliding groove under the drive of the first lead screw. The first slider is connected to the upper and lower die connecting rods via the first motion transmission shaft. A first lead screw passes through the first slider, and a first gear pair is installed at one end of the first lead screw. The first lead screw is rotated via the first gear pair to adjust the position of the first slider in the first sliding groove, thereby changing the relative movement amplitude between the upper and lower sliding platforms driven by the first slider and the upper and lower die connecting rods. The cam device is connected to the feed rocker arm via a fork-head angle lever mechanism. The fork-head angle lever mechanism includes a fork-head angle lever, a second lead screw, a second slider, a second motion transmission shaft, a second gear pair, a second shaft, and a second support. The fork-head angle lever includes a second fork head and a corner portion. One end of the corner portion is integral with the second fork head, and the corner is hinged to the second support via the second shaft. The other end of the corner portion has a second groove extending to the corner. The second slider is installed in the second groove and connected to the second lead screw thread pair, allowing it to move along the groove under the drive of the second lead screw. The second slider is connected to the feed rocker arm via the second motion transmission shaft. A second gear pair is installed at one end of the second lead screw, which rotates the second lead screw to adjust the position of the second slider in the second groove, thereby changing the range of motion of the horizontal slide table driven by the second slider and the feed rocker arm. The cam device is provided with a first cam and a second cam for connecting to the first fork head and the second fork head respectively. Of the first cam and the second cam, at least the first cam is configured to satisfy: The acceleration of the first cam is A1, its velocity is V1, and its travel distance is S1, where... The acceleration is designed in segments according to a linear equation, which is: A1=C1X+C2; The velocity is designed according to a parabolic equation, which is: V1=C1X 2 +C2X+C3; The curved travel is designed according to a cubic equation, which is: S1=C1X 3 +C2X 2 +C3X+C4; The above-mentioned curve stroke is selected to form the cam profile of the first cam, so that the first cam starts at zero speed and zero acceleration and stops at zero speed and zero acceleration.

[0009] The relevant content of this invention is explained as follows: 1. Through the implementation of the above-mentioned technical solution of the present invention, and through the study of the problems existing in the use of existing fin punching machines, and after repeated research and design, the fin forming machine of the present invention with no impact and adjustable motion amplitude was designed. The fin forming machine of the present invention specifically adds a fork head straight shank lever mechanism and a fork head corner lever mechanism. In the fork head straight shank lever mechanism, the fixed amplitude vertical motion transmitted from the cam to the fork head by the position adjustment of the first motion transmission shaft is converted into vertical motion of different amplitudes by adjusting the position. The first motion transmission shaft transmits the vertical motion to the upper slide and the lower slide respectively through the upper and lower die connecting rods. In the fork head corner lever mechanism, the adjustable second motion transmission shaft can convert the vertical motion transmitted from the cam to the fork head by the cam into horizontal motion, and the fixed amplitude vertical motion transmitted from the cam to the fork head by the cam is converted into horizontal motion by adjusting the position. The second motion transmission shaft transmits horizontal motion to the smooth table via a feed rocker arm, allowing the mold to complete the pressing and forming process of the fins. The fin forming machine of this invention also features an inventive redesign of the cam profiles for driving the upper and lower sliding tables and the horizontal sliding table in the cam device. The original cam profiles for driving the upper and lower sliding tables and the horizontal sliding table were designed as a simple combination of circular arcs and straight line segments. At a constant speed (actual fluctuations are negligible), the cam's transmission to the upper and lower sliding tables via the upper and lower mold connecting rods could not start and stop at zero speed and zero acceleration. However, in the fin forming machine of this invention, the new first cam driving the upper and lower sliding tables uses the aforementioned curved stroke to form the cam profile of the first cam, enabling the first cam to start and stop at zero speed and zero acceleration, thus eliminating motion impact, avoiding impact forces between structural components, avoiding impact noise, and reducing motion energy loss.

[0010] 2. In the above technical solution, both the first gear pair and the second gear pair are gear adjustment devices. Both the first gear pair and the second gear pair include an adjustment shaft and two bevel gears. The two bevel gears mesh to form a gear transmission pair. One bevel gear is equipped with the adjustment shaft and the other bevel gear is equipped with a lead screw. Rotating the adjustment shaft drives the gear transmission pair to rotate, thereby driving the lead screw to rotate. The adjustment method is simple and reliable.

[0011] 3. In the above technical solution, the forming machine further includes a rocker arm, an electrical control box, a spindle box, a gearbox, an electric motor, an oil pump device, a clutch, and a lubricating oil distributor, all positioned and mounted on the machine frame. The electric motor outputs power, which is transmitted to the spindle box via the gearbox. The spindle box drives the cam device to rotate. The first cam in the cam device drives the upper and lower slides to move up and down via the upper mold connecting rod. The second cam in the cam device drives the horizontal slide to move horizontally via the feed rocker arm.

[0012] 4. In the above technical solution, the corner part is an L-shaped structure, and it is a right-angled L-shape.

[0013] 5. In the above technical solution, the cam device adopts an arithmetic cam group.

[0014] 6. In the above technical solution, the acceleration of the second cam is A2, the velocity is V2, and the curve stroke is S2, wherein, The acceleration is designed in segments according to a linear equation, which is: A2=C1X+C2; The velocity is designed according to a parabolic equation, which is: V2=C1X 2 +C2X+C3; The curve travel is designed according to a cubic equation, which is: S2=C1X 3 +C2X 2 +C3X+C4; The above-mentioned curve stroke is selected to form the cam profile of the second cam, so that the second cam starts at zero speed and zero acceleration and stops at zero speed and zero acceleration.

[0015] 7. In this invention, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," "fixing," etc., 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, 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, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0016] 8. In this invention, the terms “center,” “upper,” “lower,” “axial,” “bottom,” “inner,” “outer,” etc., indicate the orientation or positional relationship based on the orientation or positional assembly relationship shown in the drawings. They are only for the convenience of describing this application and simplifying the description, and do not 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 application.

[0017] 9. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0018] Due to the application of the above-mentioned solution, the present invention has the following advantages and effects compared with the prior art: 1. In the fin forming machine of the present invention, a fork head straight handle lever mechanism and a fork head corner lever mechanism are specifically added. The fork head straight handle lever mechanism, through a position-adjustable first motion transmission shaft, converts the fixed-amplitude vertical motion transmitted from the cam to the fork head into vertical motions of different amplitudes by adjusting its position. The first motion transmission shaft transmits the vertical motion to the upper slide table and the lower slide table respectively via upper and lower mold connecting rods. The fork head corner lever mechanism, through a position-adjustable second motion transmission shaft, converts the vertical motion transmitted from the cam to the fork head into horizontal motion, and through position adjustment, converts the fixed-amplitude vertical motion transmitted from the cam to the fork head into horizontal motions of different amplitudes. The motion transmission shaft transmits the horizontal motion to the smooth table via a feed rocker arm. The above configuration allows the movement amplitude of the upper slide table and the horizontal slide table to be controlled by the fork head straight handle lever mechanism and the fork head corner lever mechanism, without the need for mechanical impact limit blocks for adjustment and limitation, thus avoiding mechanical impact noise and impact force between structural components. 2. In the fin forming machine of the present invention, the cam profile of the cam device driving the upper and lower sliding tables and the horizontal sliding table has been redesigned inventively. The original cam profile of the driving sliding table for vertical and horizontal movement was designed as a simple combination of circular arc and straight line segments. Under uniform speed (actual fluctuation is negligible), the cam can not start and stop at zero speed and zero acceleration when transmitting the motion and return of the upper and lower sliding tables through the upper and lower die connecting rods. However, in the fin forming machine of the present invention, the first cam of the new driving upper and lower sliding tables selects the above-mentioned curved stroke to form the cam profile of the first cam, so that the first cam starts at zero speed and zero acceleration and stops at zero speed and zero acceleration, thereby eliminating motion impact, avoiding impact force between structural components, avoiding impact noise, reducing motion energy loss, improving production efficiency, and extending equipment life. Attached Figure Description

[0019] Appendix Figure 1 This is a schematic diagram of the general structural form of a fin; Appendix Figure 2 A simplified diagram of a traditional finned punch press (perspective 1); Appendix Figure 3 A simplified diagram of a traditional finned punch press (perspective 2); Appendix Figure 4 This is a schematic diagram of a fin forming machine according to an embodiment of the present invention (view 1). Appendix Figure 5 This is a schematic diagram of a fin forming machine according to an embodiment of the present invention (view 2). Appendix Figure 6 This is a schematic diagram of the fork head corner lever mechanism in a fin forming machine according to an embodiment of the present invention; Appendix Figure 7This is a schematic diagram of the fork head straight handle lever mechanism in a fin forming machine according to an embodiment of the present invention; Appendix Figure 8 This is a schematic diagram of the profile projection of the original lifting cam; Appendix Figure 9 This is a schematic diagram of the profile projection of the first cam in a fin forming machine according to an embodiment of the present invention; Appendix Figure 10 This is a cross-sectional schematic diagram of the first cam in a fin forming machine according to an embodiment of the present invention; Appendix Figure 11 This is a schematic diagram showing the partial profile development of the original lifting cam and the first cam; Appendix Figure 12 This is a schematic diagram of the mathematical relationship between the acceleration (force), velocity, and stroke of the first cam and the second cam in an embodiment of the present invention. Appendix Figure 13 This is a schematic diagram of the profile projection of the original translation cam; Appendix Figure 14 This is a schematic diagram of the profile projection of the second cam in a fin forming machine according to an embodiment of the present invention.

[0020] The parts shown in the above attached diagram are illustrated below: 1. Frame body 2. Upper casing 3 Upper slide 4. Upper mold connecting rod 5. Shaping table 6. Insert the joystick 7. Slide down platform 8 rocker arm 9. Electrical control box 10 Spindle box 11 Cam device 11-1 First Cam 11-2 Second Cam 12 gearbox 13 Electric motors 14 Oil pump unit 15. Clutch 16 Lubricating oil distributor 17. Fork-head angle lever mechanism 17-1 Fork-head angle lever 17-11 Second Fork Head 17-12 Corner 17-13 Second Slide 17-2 Second Lead Screw 17-3 Second Slider 17-4 Second Motion Transmission Shaft 17-5 Second Gear Pair 17-6 Second Axis 17-7 Second Support 18. Fork-head straight lever mechanism 18-1 Fork-head straight shank lever 18-11 First Fork Head 18-12 straight handle 18-13 First Slide 18-2 First Lead Screw 18-3 First Slider 18-4 First Motion Transmission Shaft 18-5 First Gear Pair 18-6 First Axis 18-7 First Support 19 Horizontal sliding table 801 Original lifting cam 802 Original translation cam 900 fins. Detailed Implementation

[0021] To make the above-mentioned objectives, features, and advantages of this application more apparent and understandable, the specific embodiments of this application are described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of this application. However, this application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of this application. Therefore, this application is not limited to the specific embodiments disclosed below.

[0022] As attached Figure 4 Appendix Figure 5 As shown, Embodiment 1 of the present invention proposes a fin forming machine for stamping and forming fins in a plate-fin heat exchanger. The fin forming machine includes a frame body 1, an upper housing 2, an upper slide table 3, an upper die connecting rod 4, a forming table 5, a feeding rocker arm 6, a lower slide table 7, a rocker arm 8, an electrical control box 9, a spindle box 10, a cam device 11, a gearbox 12, a motor 13, an oil pump device 14, a clutch 15, a lubricating oil distributor 16, a horizontal slide table 19, and other components. A fork-head straight handle lever mechanism 18 is provided at the connection between the cam device 11 and the upper and lower die connecting rods. A fork-head angle lever mechanism 17 is provided at the connection between the cam device 11 and the feed rocker arm 6; the cam device 11 is provided with a first cam 11-1 and a second cam 11-2; the motor 13 outputs power, which is converted and transmitted to the main spindle box 10 via the gearbox 12, and the main spindle box 10 drives the cam device 11 to rotate. The first cam 11-1 in the cam device 11 drives the upper and lower slide tables 7 to move up and down through the upper mold connecting rod 4, and the second cam 11-2 in the cam device 11 drives the horizontal slide table 19 to move horizontally through the feed rocker arm 6.

[0023] In an embodiment of the present invention, the cam device 11 is connected to the upper and lower mold connecting rods via a fork-head straight handle lever mechanism 18; the fork-head straight handle lever mechanism 18 includes a fork-head straight handle lever, a first lead screw 18-2, a first slider 18-3, a first motion transmission shaft 18-4, a first gear pair 18-5, a first shaft 18-6, and a first support 18-7. The fork-head straight handle lever includes a first fork head 18-11 and a straight handle portion 18-12. One end of the straight handle portion 18-12 is integral with the first fork head 18-11, and the other end is hinged to the first support 18-7 via the first shaft 18-6. A first sliding groove 1 is provided on the straight handle portion 18-12 along the length direction of the straight handle portion 18-12. 8-13, the first slider 18-3 is installed in the first slide groove 18-13 and is threadedly connected to the first lead screw 18-2, and can move along the first slide groove under the drive of the first lead screw 18-2; the first slider 18-3 is connected to the upper and lower mold connecting rods through the first motion transmission shaft 18-4; the first lead screw 18-2 is threaded through the first slider 18-3, and a first gear pair 18-5 is installed at one end of the first lead screw 18-2. The first lead screw 18-2 is rotated through the first gear pair 18-5 to adjust the position of the first slider 18-3 in the first slide groove 18-13, thereby changing the relative movement amplitude between the upper slide table 3 and the lower slide table 7 driven by the first slider 18-3 to the upper and lower mold connecting rods. In the fork head straight lever mechanism 18, the position-adjustable first motion transmission shaft 18-4 transforms the fixed amplitude motion in the up and down direction transmitted by the cam to the fork head into up and down motion of different amplitudes through position adjustment. The first motion transmission shaft 18-4 transmits the up and down motion to the upper slide 3 and the lower slide 7 respectively through the upper and lower mold connecting rods.

[0024] In an embodiment of the present invention, the cam device 11 and the feed rocker arm 6 are connected by a fork-head angle lever mechanism 17; the fork-head angle lever mechanism 17 includes a fork-head angle lever, a second lead screw 17-2, a second slider 17-3, a second motion transmission shaft 17-4, a second gear pair 17-5, a second shaft 17-6, and a second support 17-7. The fork-head angle lever includes a second fork head 17-11 and a corner portion 17-12. One end of the corner portion 17-12 is integral with the second fork head 17-11, and the corner is hinged to the second support 17-7 via the second shaft 17-6. A second groove 17-13 extending to the corner is provided on the other end of the corner portion 17-12. The second slider 17-3 is installed in the second groove 17-13 and is threadedly connected to the second lead screw 17-2, which can be connected to the second lead screw 17-2. Driven by the second slider 17-3, the second slider 17-3 is connected to the feed rocker 6 via the second motion transmission shaft 17-4. A second gear pair 17-5 is installed at one end of the second lead screw 17-2. The second lead screw 17-2 is rotated via the second gear pair 17-5 to adjust the position of the second slider 17-3 in the second slide groove 17-13, thereby changing the range of motion of the horizontal slide table 19 driven by the second slider 17-3 and the feed rocker 6. In the fork head corner lever mechanism 17, the position-adjustable second motion transmission shaft 17-4 can convert the vertical motion transmitted from the cam to the fork head into horizontal motion. Furthermore, by adjusting the position, the fixed vertical motion transmitted from the cam to the fork head can be converted into different horizontal motions. The second motion transmission shaft 17-4 transmits the horizontal motion to the smooth table via the feed rocker 6.

[0025] In an embodiment of the present invention, the cam device 11 employs an arithmetic progression cam set. The cam device 11 is provided with a first cam 11-1 and a second cam 11-2 for connecting to the first fork head 18-11 and the second fork head 17-11, respectively. Of the first cam 11-1 and the second cam 11-2, at least the first cam 11-1 is configured to satisfy the following: The acceleration of the first cam is A1, its velocity is V1, and its travel distance is S1, where... The acceleration is designed in segments according to a linear equation, which is: A1=C1X+C2; The velocity is designed according to a parabolic equation, which is: V1=C1X 2 +C2X+C3; The curved travel is designed according to a cubic equation, which is: S1=C1X 3 +C2X 2 +C3X+C4; The above-mentioned curve stroke is selected to form the cam profile of the first cam 11-1, so that the first cam 11-1 starts with zero speed and zero acceleration and stops with zero speed and zero acceleration.

[0026] Specifically, the acceleration of the second cam is A2, its velocity is V2, and its travel distance is S2, where... The acceleration is designed in segments according to a linear equation, which is: A2=C1X+C2; The velocity is designed according to a parabolic equation, which is: V2=C1X 2 +C2X+C3; The curve travel is designed according to a cubic equation, which is: S2=C1X 3 +C2X 2 +C3X+C4; The above-mentioned curve stroke is selected to form the cam profile of the second cam 11-2, so that the second cam 11-2 starts with zero speed and zero acceleration, and stops with zero speed and zero acceleration.

[0027] In this embodiment of the invention, C1, C2, C3, and C4 are constants of their respective equations, and the total travel distance is designed as needed.

[0028] Through the implementation of the above embodiments of the present invention, and through the study of the problems existing in the use of existing fin punching machines, and after repeated research and design, the fin forming machine of the present invention with no impact and adjustable motion amplitude was designed. The fin forming machine of the present invention specifically adds a fork head straight lever mechanism 18 and a fork head corner lever mechanism 17. In the fork head straight lever mechanism 18, the position-adjustable first motion transmission shaft 18-4 converts the fixed amplitude vertical motion transmitted from the cam to the fork head into vertical motion of different amplitudes by adjusting its position. The first motion transmission shaft 18-4 transmits the vertical motion to the upper slide 3 and the lower slide 7 respectively through the upper and lower die connecting rods. In the fork head corner lever mechanism 17, the position-adjustable second motion transmission shaft 17-4 converts the vertical motion transmitted from the cam to the fork head into horizontal motion, and by adjusting its position, converts the fixed amplitude vertical motion transmitted from the cam to the fork head into horizontal motion of different amplitudes. With the same amplitude of motion, the second motion transmission shaft 17-4 transmits the horizontal motion to the smooth table through the feed rocker 6, so that the mold can complete the pressing and forming process of the fins. In the fin forming machine of the present invention, the cam profile of the driving upper and lower slide tables 7 and the driving horizontal slide table 19 in the cam device 11 has been redesigned inventively. The original cam profile of the driving slide table for the up and down movement and the horizontal movement was designed as a combination of simple circular arc and straight line segments. Under uniform speed (actual fluctuation is small and negligible), the process and return of the cam transmitted to the upper and lower slide tables 7 through the upper and lower mold connecting rods cannot start and stop at zero speed and zero acceleration. However, in the fin forming machine of the present invention, the new first cam 11-1 driving the upper and lower slide tables 7 selects the above-mentioned curved stroke to form the cam profile of the first cam 11-1, so that the first cam 11-1 starts at zero speed and zero acceleration and stops at zero speed and zero acceleration, thereby eliminating motion impact, avoiding impact force between structural parts, avoiding impact noise, and reducing motion energy loss.

[0029] In the above embodiments of the present invention, the first gear pair 18-5 and the second gear pair 17-5 are both gear adjustment devices. The first gear pair 18-5 and the second gear pair 17-5 each include an adjustment shaft and two bevel gears. The two bevel gears mesh to form a gear transmission pair. One bevel gear is equipped with the adjustment shaft and the other bevel gear is equipped with a lead screw. Rotating the adjustment shaft drives the gear transmission pair to drive the lead screw to rotate, so that the sliding block on the lead screw can be adjusted in position along the slide groove. The adjustment method is simple and reliable.

[0030] In the cam device 11, the fin forming machine of this embodiment of the invention has made an inventive redesign of the cam profiles for driving the upper and lower sliding tables 7 and driving the horizontal sliding table 19. The original cam profile for driving the upper and lower sliding tables 7 to move up and down was designed as a simple combination of circular arcs. The original lifting cam 801 profile for driving the upper and lower sliding tables 7 is shown below. Figure 8Under uniform rotational speed (actual fluctuations are negligible), the cam's transmission to the upper and lower sliding platforms 7 via the guide rod cannot start and stop at zero speed and zero acceleration. The new lifting cam (first cam 11-1) driving the upper and lower sliding platforms 7 starts and stops at zero speed and zero acceleration. The profile projection is as follows: Figure 9 As shown, the partial unfolded diagrams of the original lifting cam profile 801 and the new lifting cam profile are as follows. Figure 11 As shown, the mathematical relationship between the acceleration (force), velocity, and stroke of the new lifting cam (first cam 11-1) profile is as follows: Figure 12 As shown, the acceleration of the first cam is A1, its velocity is V1, and its curved stroke is S1. The acceleration is designed in segments according to the linear equation A1=C1X+C2 (C1 and C2 are different for each segment, the same below), and the velocity is designed according to the parabolic equation V1=C1X. 2 +C2X+C3, the total stroke is designed as needed, and the curve stroke alignment is designed according to a cubic equation: S1=C1X 3 +C2X 2 The +C3X+C4 design eliminates motion impact, avoids impact forces between structural components, reduces impact noise, and minimizes motion energy loss. Furthermore, the cam uses an arithmetic cam assembly, which, in conjunction with the fork lever, prevents the return stroke of the upper and lower slides from relying on spring thrust, thus freeing them from the constraints of system elasticity and mass inertia, thereby increasing speed.

[0031] The original translation cam 802 type line that drives the horizontal slide 19 to move forward and backward is shown in the figure. Figure 13 The cam profile of the previous method was designed as a combination of arcs and straight lines, meaning it did not start with zero speed and zero acceleration. This inevitably led to motional impacts between structural components during movement. Furthermore, the translational range of the smooth table was limited by mechanically impacting and stopping blocks, meaning it could not stop at zero speed and zero acceleration, inevitably resulting in mechanical impact noise and force between structural components. In contrast, the cam profile of the drive horizontal slide 19 of this invention is designed to start and stop at zero speed and zero acceleration, and the cam uses an arithmetic progression cam assembly. The cam profile projection is as follows: Figure 14 As shown, the mathematical relationship between acceleration (force), velocity, and stroke is also as follows: Figure 12 As shown, the acceleration of the second cam is A2, the velocity is V2, and the curved stroke is S2. The acceleration is designed piecewise according to a linear equation: A2 = C1X + C2; the velocity is designed according to a parabolic equation: V2 = C1X. 2 +C2X+C3; The curve travel is designed according to a cubic equation, which is: S2=C1X 3 +C2X 2+C3X+C4; This avoids mechanical impact noise and mechanical impact force between structural components, improves production efficiency, and extends equipment life.

[0032] The above embodiments are only for illustrating the technical concept and features of the present invention, and are intended to enable those skilled in the art to understand the content of the present invention and implement it accordingly. They should not be construed as limiting the scope of protection of the present invention. All equivalent changes or modifications made in accordance with the spirit and essence of the present invention should be covered within the scope of protection of the present invention.

Claims

1. A fin forming machine for stamping fins in a plate-fin heat exchanger, the forming machine comprising a frame (1), an upper housing (2), an upper slide (3), upper and lower die connecting rods, a forming table (5), a feed rocker arm (6), a lower slide (7), a cam device (11), and a horizontal slide (19), wherein the cam device (11) is connected to either the upper slide (3) or the lower slide (7) via the upper and lower die connecting rods, and the cam device (11) is connected to the horizontal slide (19) via the feed rocker arm (6), characterized in that: The cam device (11) is connected to the upper and lower mold connecting rods via a fork-head straight handle lever mechanism (18). The fork-head straight handle lever mechanism (18) includes a fork-head straight handle lever, a first lead screw (18-2), a first slider (18-3), a first motion transmission shaft (18-4), a first gear pair (18-5), a first shaft (18-6), and a first support (18-7). The fork-head straight handle lever includes a first fork head (18-11) and a straight handle portion (18-12). One end of the straight handle portion (18-12) is integral with the first fork head (18-11), and the other end is hinged to the first support (18-7) via the first shaft (18-6). A first sliding groove (18-13) is provided on the straight handle portion (18-12) along the length direction of the straight handle portion (18-12). The first slider (18-3) is installed in the first slide groove (18-13) and is threadedly connected to the first lead screw (18-2). It can move along the first slide groove under the drive of the first lead screw (18-2). The first slider (18-3) is connected to the upper and lower mold connecting rods through the first motion transmission shaft (18-4). The first lead screw (18-2) is threaded through the first slider (18-3). The first gear pair (18-5) is installed at one end of the first lead screw (18-2). The first lead screw (18-2) is rotated through the first gear pair (18-5) to adjust the position of the first slider (18-3) in the first slide groove (18-13), thereby changing the relative movement amplitude between the upper slide (3) and the lower slide (7) driven by the first slider (18-3) to the upper and lower mold connecting rods. The cam device (11) is connected to the feed rocker arm (6) via a fork-head angle lever mechanism (17); the fork-head angle lever mechanism (17) includes a fork-head angle lever, a second lead screw (17-2), a second slider (17-3), a second motion transmission shaft (17-4), a second gear pair (17-5), a second shaft (17-6), and a second support (17-7). The fork-head angle lever includes a second fork head (17-11) and a corner portion (17-12). One end of the corner portion (17-12) is integral with the second fork head (17-11), and the corner is hinged to the second support (17-7) via the second shaft (17-6). The other end of the corner portion (17-12) has an extension extending to the pivot. The second slide (17-13) is located at the corner. The second slider (17-3) is installed in the second slide (17-13) and is connected to the threaded pair of the second lead screw (17-2). It can move along the slide under the drive of the second lead screw (17-2). The second slider (17-3) is connected to the feed rocker (6) through the second motion transmission shaft (17-4). A second gear pair (17-5) is installed at one end of the second lead screw (17-2). The second lead screw (17-2) is rotated through the second gear pair (17-5) to adjust the position of the second slider (17-3) in the second slide (17-13), thereby changing the movement amplitude of the horizontal slide (19) driven by the second slider (17-3) and the feed rocker (6). The cam device (11) is provided with a first cam (11-1) and a second cam (11-2) for connecting to the first fork head (18-11) and the second fork head (17-11) respectively. Of the first cam (11-1) and the second cam (11-2), at least the first cam (11-1) is configured to satisfy: The acceleration of the first cam (11-1) is A1, its velocity is V1, and its travel distance is S1. The acceleration is designed in segments according to a linear equation, which is: A1=C1X+C2; The velocity is designed according to a parabolic equation, which is: V1=C1X 2 +C2X+C3; The curved travel is designed according to a cubic equation, which is: S1=C1X 3 +C2X 2 +C3X+C4; C1, C2, C3, and C4 are constants in the equations. The above-mentioned curve stroke is selected to form the cam profile of the first cam (11-1), so that the first cam (11-1) starts with zero speed and zero acceleration and stops with zero speed and zero acceleration.

2. The fin forming machine according to claim 1, characterized in that: Both the first gear pair (18-5) and the second gear pair (17-5) are gear adjustment devices. Both the first gear pair (18-5) and the second gear pair (17-5) include an adjustment shaft and two bevel gears. The two bevel gears mesh to form a gear transmission pair. One bevel gear is equipped with the adjustment shaft and the other bevel gear is equipped with a lead screw. Rotating the adjustment shaft drives the gear transmission pair to rotate, thereby driving the lead screw to rotate.

3. The fin forming machine according to claim 1, characterized in that: The forming machine also includes a rocker arm (8), an electrical control box (9), a main shaft box (10), a gearbox (12), an electric motor (13), an oil pump device (14), a clutch (15), and a lubricating oil distributor (16) positioned and installed on the frame body (1). The electric motor (13) outputs power, which is transmitted to the main shaft box (10) via the gearbox (12). The main shaft box (10) drives the cam device (11) to rotate. The first cam (11-1) in the cam device (11) drives the upper and lower slides (7) to move up and down via the upper mold connecting rod (4). The second cam (11-2) in the cam device (11) drives the horizontal slide (19) to move horizontally via the feed rocker arm (6).

4. The fin forming machine according to claim 1, characterized in that: The corner section (17-12) has an L-shaped structure.

5. The fin forming machine according to claim 1, characterized in that: The cam device (11) uses an arithmetic cam group.

6. The fin forming machine according to claim 1, characterized in that: The acceleration of the second cam is A2, its velocity is V2, and its travel distance is S2, where... The acceleration is designed in segments according to a linear equation, which is: A2=C1X+C2; The velocity is designed according to a parabolic equation, which is: V2=C1X 2 +C2X+C3; The curve travel is designed according to a cubic equation, which is: S2=C1X 3 +C2X 2 +C3X+C4; C1, C2, C3, and C4 are constants in the equations. The above-mentioned curve stroke is selected to form the cam profile of the second cam (11-2), so that the second cam (11-2) starts with zero speed and zero acceleration and stops with zero speed and zero acceleration.

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