Servo cam mechanical equipment cam optimization design method and optimized cam

Abstract

A cam optimization design method and an optimized cam for servo cam mechanical equipment relate to the technical field of cam optimization. A cam profile curve segment with a pressure angle greater than an allowable pressure angle is replaced with a replacement cam curve segment with a smaller pressure angle, and a new cam curve is generated by fitting to improve the load-bearing and wear-resistant performance of the cam. After the original cam is worn, it is only necessary to replace the cam curve as needed to produce a replacement curve cam block, and assemble it with the original cam block to obtain an optimized cam, thereby reducing the cost of cam replacement.

Description

Technical Field

[0001] The present invention belongs to the technical field of cam optimization, and in particular relates to a cam optimization design method for servo cam mechanical equipment and an optimized cam. Background Art

[0002] In production and life, friction will cause material wear, which not only consumes a large amount of materials, but also damages equipment components and engineering structures. The cam mechanism is one of the typical commonly used mechanisms. The cam and the follower are often in high-pair contact, usually working under high temperature, high speed and variable pressure, which can easily cause severe friction and wear on the cam working surface. For example, the patent document CN113492189A discloses a cam-driven mechanical press. As a high-precision stamping mechanical equipment, the cam wear will cause the displacement of the follower to change. When the long-term cumulative error exceeds the limit, the stamping part will shake during the forming process, resulting in poor forming quality, which will reduce the working accuracy and working life of the equipment, affecting not only production quality but also economic benefits. For this type of mechanical equipment with a cam direct drive, the wear resistance and load-bearing capacity of the cam have a great influence on the accuracy and efficiency of the equipment. In addition, the cam needs to be replaced after reaching its wear life. For large equipment such as a press, replacement is not only complicated, but also has high maintenance costs. Summary of the Invention

[0003] The purpose of the present invention is to address the shortcomings of the existing technology and provide a servo cam mechanical equipment cam optimization design method and optimized cam, which replaces the cam profile curve segment with a pressure angle greater than the allowable pressure angle with a replacement cam curve segment with a smaller pressure angle according to working requirements to improve the wear resistance and load-bearing capacity of the cam; after the original cam is worn, it is only necessary to replace the cam curve as needed to make a replacement curve cam block, and assemble it with the original cam block to obtain an optimized cam, thereby reducing the cost of cam replacement.

[0004] In order to solve the above technical problems, the present invention adopts the following technical solutions:

[0005] A cam optimization design method for a servo cam mechanical device comprises the following steps:

[0006] Step 1: Draw the original cam profile after wear;

[0007] Step 2: Draw the pressure angle-cam angle variation curve during the entire motion cycle of the original cam and the original displacement-cam angle curve of the follower in contact with the original cam high pair. The pressure angle is the angle between the follower motion direction and the normal direction of the contact point between the follower and the original cam.

[0008] Step 3: Set the allowable pressure angle and record the cam angle range of the original cam whose pressure angle is greater than the allowable pressure angle during the entire motion cycle. This angle range is defined as the marked cam angle.

[0009] Step 4: Based on the cam stroke corresponding to the marked cam angle, the original displacement of the follower corresponding to both ends of the marked cam angle, and the cam angle, combined with different follower motion laws, multiple replacement cam curve segments are obtained;

[0010] Step 5: Draw the pressure angle-cam rotation angle curves of the various replacement cam curve segments obtained in step 4, select the replacement cam curve segments with a pressure angle not greater than the allowable pressure angle, and fit them to the cam profile outside the cam rotation angle range of the original cam mark;

[0011] Step 6: According to the replacement cam curve segment fitted in step 5, a replacement curve cam block is made, and the replacement curve cam block is assembled with the original cam block outside the cam angle range of the original cam mark to obtain an optimized cam.

[0012] Preferably, in step 4, the motion law of the follower includes a linear polynomial motion law, a quadratic polynomial motion law, a quintic polynomial motion law, a cosine motion law, a sine motion law, and a motion law of a combination of two or more of the above motion laws.

[0013] It should be noted that the cam curve itself is obtained from the motion law of the follower. The various replacement cam curve segments are obtained by substituting the above conditions into the displacement equations of different followers. The unknown coefficients can be solved to obtain a certain follower displacement equation. According to the displacement equation, the coordinates of the cam curve, that is, the cam contour line, can be obtained. In the embodiment, this step is programmed by writing a program.

[0014] Preferably, the follower motion equation is as follows:

[0015] Linear polynomial motion law: s=C0+C1δ (1-1)

[0016] Quadratic polynomial motion law: s=C0+C1δ+C2δ 2 (1-2)

[0017] Cosine acceleration motion law:

[0018] The equation of motion during the push stroke is: s=h[1-cos(πδ / δ0)] / 2 (1-3)

[0019] The equation of motion during the return stroke is: s = h[1 + cos(πδ / δ0′)] / 2 (1-4)

[0020] Sinusoidal acceleration motion law:

[0021] The equation of motion during the push-off is: s = h[(δ / δ0)-sin(2πδ / δ0) / (2π)] (1-5)

[0022] The equation of motion during the return stroke is: s = h[1-(δ / δ0′)+sin(2πδ / δ0′) / (2π)] (1-6)

[0023] In the above formula, C1, C2, C3, ..., C n is the unknown coefficient, ω is the angular velocity, h is the displacement of the follower, δ is the cam angle, δ0 is the cam motion angle during the push stroke, and δ0′ is the cam motion angle during the return stroke.

[0024] Preferably, in step 1, the original cam contour line is drawn based on the original cam structural parameters after wear and the original motion law of the follower in contact with the original cam high pair, wherein the cam structural parameters include the cam base circle radius, thrust motion angle, distal repose angle, return motion angle, proximal repose angle, maximum thrust displacement and cam speed.

[0025] Preferably, in step 5, if there are multiple replacement cam curve segments with a pressure angle not greater than the allowable pressure angle, the replacement cam curve segment with a smaller pressure angle is selected.

[0026] An optimized cam for a servo cam mechanical device comprises: an original cam block and a replacement curved cam block assembled into a complete cam, and a locking ring for locking the original cam block and the replacement curved cam block; first bosses are provided on both axial side walls of the original cam block; a positioning boss is provided on the original cam block at the position where it is assembled with the replacement curved cam block; a positioning groove is provided on the replacement curved cam block that cooperates with the positioning boss; second bosses are provided on both axial ends of the replacement curved cam block; the outer end surface of the first boss and the second boss after being assembled is a cylindrical surface, and the locking ring cooperates and locks on the cylindrical surface;

[0027] The above-mentioned original cam blocks and replacement curve cam blocks are designed by the servo cam mechanical equipment cam optimization design method described in any one of claims 1 to 4.

[0028] Preferably, the locking ring is locked on the first boss and the second boss by threaded engagement; a notch is provided on the locking ring for easy rotational installation.

[0029] Preferably, the first boss is provided with a matching groove that matches with the second boss.

[0030] Preferably, the positioning boss is fan-shaped and located in the middle of the original cam block in the axial direction.

[0031] Preferably, the axial thickness of the positioning boss is not less than 1 / 2 of the thickness of the original cam block; the outer diameter of the positioning boss is less than 2 / 3 of the maximum diameter of the original cam block, and greater than 1 / 2 of the sum of the maximum diameter and minimum diameter of the original cam block.

[0032] Preferably, the original cam block, the replacement curve cam block and the locking ring are all made of Gcr15 steel.

[0033] Among them, the servo cam mechanical equipment can rely on the servo motor to adjust the speed and acceleration motion curve of the follower. Therefore, fitting the cam profile curve segment only needs to ensure the consistency of the displacement before and after the cam profile curve fitting.

[0034] Compared with the prior art, the beneficial effects of the present invention are: by replacing the cam profile curve with a smaller pressure angle and fitting to generate a new cam curve, the load-bearing and wear-resistant performance of the cam is improved, and the cam blocks are replaced with replacement curve cam blocks according to the replacement cam curve, thereby reducing the cam replacement cost, and will not change the stroke of the follower, and can be directly assembled and applied on the mechanical equipment in use. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] Figure 1 A schematic diagram of the main interface for obtaining the original cam in a preferred embodiment of the present invention;

[0036] Figure 2 Schematic diagram of the displacement curve of the slider in the preferred embodiment of the present invention;

[0037] Figure 3 Schematic diagram of the original cam pressure angle curve in the preferred embodiment of the present invention;

[0038] Figure 4 This is a schematic diagram of the main interface for changing the cam curve in a preferred embodiment of the present invention;

[0039] Figure 5 Schematic diagram of a pressure angle curve for replacing a cam curve segment in a preferred embodiment of the present invention;

[0040] Figure 6 A comparison diagram of the original cam and the fitted cam profiles in a preferred embodiment of the present invention;

[0041] Figure 7 Schematic diagram comparing the pressure angle curves of the original cam and the fitted cam in a preferred embodiment of the present invention;

[0042] Figure 8 This is a schematic structural diagram of the original cam blocks in a preferred embodiment of the present invention;

[0043] Figure 9 This is a structural diagram of replacing the curved cam blocks in a preferred embodiment of the present invention;

[0044] Figure 10 This is a schematic structural diagram of an optimized cam in a preferred embodiment of the present invention;

[0045] Figure 11 This is a schematic structural diagram of a locking ring in a preferred embodiment of the present invention;

[0046] Figure 12 This is a schematic diagram of the assembly of the optimized cam in the preferred embodiment of the present invention;

[0047] Among them, 1. Original cam block, 11. Positioning boss, 12. Axial keyway, 13. First boss, 2. Replacement curve cam block, 21. Second boss, 22. Positioning groove, 3. Optimized cam, 31. External thread, 4. Locking ring, 41. Internal thread, 42. Notch, 5. Flat key, 6. Camshaft, 7. Flat key keyway. DETAILED DESCRIPTION

[0048] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. All other embodiments obtained by ordinary technicians in this field based on the embodiments of the present invention without making any creative efforts shall fall within the scope of protection of the present invention.

[0049] It should be noted that, in the absence of conflict, the embodiments of the present invention and the features in the embodiments may be combined with each other.

[0050] The present invention will be further described below with reference to specific examples, but they are not intended to limit the present invention.

[0051] In the embodiments of the present invention, a single-point cam press is used as an example. The cam base radius is 115 mm, the roller radius is 30 mm, the thrust stroke angle is 150°, the distal repose angle is 30°, the return stroke angle is 120°, the proximal repose angle is 60°, the maximum thrust stroke displacement is 100 mm, and the cam speed is 600° / s. Both the roller and the slider are driven elements, and their displacement curves and motion patterns are consistent.

[0052] Utilizing the Matlab App Designer module for software programming, a cam curve acquisition software was constructed. The cam curve itself is derived from the motion law of the follower. The various cam curve segments are replaced by substituting the aforementioned conditions into the displacement equations of different follower components. The unknown coefficients can be solved to obtain a specific follower displacement equation. The coordinates of the cam curve, or cam profile, can be derived from the displacement equation. This embodiment implements this step by programming.

[0053] like Figure 1As shown; the interface includes two input parameter boxes: "Slider Motion Law Selection" and "Cam Mechanism Parameters", as well as four output options: "Draw Cam Curve", "Output Cam Coordinates", "Slider Displacement Curve", and "Pressure Angle Curve". The default unit is mm. Enter the original cam parameters in the input parameter box and click the "Draw Cam Profile" button to display the cam profile. Click "Output Cam Coordinates" to save the original cam profile curve coordinate points as a .txt file. The original cam profile curve coordinates can be used to subsequently extract the original cam profile segment that meets the allowable pressure angle. Click the "Slider Displacement Curve" button to obtain the slider motion displacement curve corresponding to the original cam profile. Click "Pressure Angle Curve" to obtain a pressure angle variation diagram for the cam throughout the entire motion cycle.

[0054] Specifically, in the software program for obtaining the original cam, the displacement s of the cam follower contact point is obtained by substituting the cam parameters into the follower displacement equation, and the displacement curve of the follower is obtained by changing the displacement with the cam rotation angle, and the cam profile coordinates are obtained by the following formulas: x = (r + s) * sin (d), y = (r + s) * cos (d), where r is the base circle radius, d is the cam rotation angle, and the pressure angle is obtained by the following formulas a = tan (ds / (rb + s)), pressure_angle = arctan (a), where ds is the first-order derivative equation of the follower displacement equation with respect to the cam rotation angle. The original cam acquisition software completes the relevant functions by building in the above equations.

[0055] In this embodiment, the drawing of the original cam contour line, the pressure angle-cam angle change curve during the entire motion cycle of the original cam, and the original displacement-cam angle curve of the follower can all be completed on the above-mentioned replacement software, greatly improving the optimization design efficiency.

[0056] Please refer to Figures 1 to 3 , input the cam mechanism parameters of the cam press in the above replacement software. To avoid the impact caused by the sudden acceleration at the beginning and end, the slider motion law is a sine motion curve, obtain the original cam profile, output the cam profile coordinates, and draw the slider displacement curve, such as Figure 2 As shown, it is used to obtain the displacement of the two ends of the replacement cam curve segment in the future, so as to achieve the same displacement at the joint during fitting. Output the pressure angle curve of the original cam, as shown Figure 3 As shown, the allowable pressure angle is set to 25°, and the cam rotation angle range exceeding the allowable pressure angle is (230°, 260°).

[0057] At the same time, MATLAB App Designer is used to build a cam curve replacement software. The software is constructed as follows: the following four follower displacement equations are built in. First, the motion law and the stroke where the replacement curve is located are selected to determine the follower displacement equation to be used. By substituting the original cam parameters, the displacements at both ends of the replacement cam curve segment, and the cam angles at both ends of the replacement cam curve segment into the equation, the unknown parameters in the equation can be solved, such as C1 and C2 in the displacement equation of the first motion law, so as to obtain a complete displacement equation. Then, as with the above-mentioned original cam acquisition software, the same pressure angle equation and cam profile equation are built in to obtain the replacement cam curve segment and the corresponding pressure angle curve.

[0058] like Figure 4 As shown, select the slider motion law type, select the cam stroke where the replacement curve is located, enter the cam angle and displacement of the cam at both ends of the replacement curve, and then, combined with the cam and roller structural parameters, click the "Draw Cam Profile" button to display the cam profile segments under each slider motion law. Click the "Draw Pressure Angle Curve" button to display the pressure angle curve of the cam profile segment. Based on the comparison between the pressure angle curve and the allowable pressure angle, determine whether to output the replacement cam curve segment for the cam. If the allowable pressure angle is met, click "Cam Coordinates" to output the coordinates of the replacement cam curve segment. These coordinates can be fitted with the coordinates of the original cam profile segment to form a new cam. If the allowable pressure angle is not met, change the slider motion law type and continue to determine until the allowable pressure angle is met.

[0059] The program for obtaining the replacement cam profile curve has four built-in motion law equations as follows:

[0060] Linear polynomial motion law: s=C0+C1δ (1-1)

[0061] Quadratic polynomial motion law: s=C0+C1δ+C2δ 2 (1-2)

[0062] Cosine acceleration motion law:

[0063] The equation of motion during the push stroke is: s=h[1-cos(πδ / δ0)] / 2 (1-3)

[0064] The equation of motion during the return stroke is: s=h[[1+cos(πδ / δ0′)] / 2 (1-4)

[0065] Sinusoidal acceleration motion law:

[0066] The equation of motion during the push-off is: s = h[(δ / δ0)-sin(2πδ / δ0) / (2π)] (1-5)

[0067] The equation of motion during the return stroke is: s = h[1-(δ / δ0′)+sin(2πδ / δ0′) / (2π)] (1-6)

[0068] In the above formula, C1, C2, C3, ..., C n is the unknown coefficient, ω is the angular velocity, h is the displacement of the follower, δ is the cam angle, δ0 is the cam motion angle during the push stroke, and δ0′ is the cam motion angle during the return stroke.

[0069] In this embodiment, select the polynomial motion law, i.e., constant velocity motion, select the return stroke, and input the cam angles (230°, 260°) and displacements at both ends of the replacement curve. The pressure angle curve of the replacement cam curve segment is obtained as follows: Figure 5 , meet the requirements, output the cam profile and coordinates, fit the cam profile segment with the cam profile outside the cam angle range of the original cam mark, and obtain the fitted new cam. The slider motion equation corresponding to the new cam is:

[0070] Push process:

[0071]

[0072]

[0073] in:

[0074]

[0075]

[0076] Near rest:

[0077] The new cam is fitted by the coordinates of the original cam profile segment and the coordinates of the replacement profile curve. The displacement at the junction is consistent, that is, the coordinate data of the two profiles at the junction are consistent. Due to the adjustability of the servo press motor output curve, the speed curve and acceleration curve of the slider movement can be adjusted by the motor output. It is only necessary to ensure the continuity of the displacement at the cam junction. The profile comparison between the original cam and the new cam is as follows: Figure 6 As shown in the figure, the pressure angle change diagram is as follows Figure 7 As shown in the figure, the comparison shows that without changing the slider displacement, the cam's pressure angle is reduced to a certain extent, thereby improving the cam's load capacity and wear resistance. By using MATLAB App Designer to build software for obtaining original cams and replacing cam curves, design efficiency can be greatly improved.

[0078] According to the above optimization design method, the optimized cam 3 is designed and manufactured, and assembled on the above cam press. Figures 8 to 10 The optimized cam 3 includes an original cam block 1, a replacement curve cam block 2, and a locking ring 4 for locking the original cam block 1 and the replacement curve cam block 2. The original cam block 1 and the replacement curve cam block 2 are assembled and merged to form a complete cam. An axial keyway 12 is provided on the circumferential surface of the inner hole of the original cam block 1, which is convenient for assembly and use with the camshaft 6.

[0079] Among them, the original cam block 1 is provided with a first boss 13 on both axial side walls, the original cam block 1 is provided with a positioning boss 11 at the position where it is assembled with the replacement curve cam block 2, and the replacement curve cam block 2 is provided with a positioning groove 22 that cooperates with the positioning boss 11. The positioning boss 11 is fan-shaped and located in the middle of the axial direction of the original cam block 1 to prevent the two cam blocks from moving back and forth. At the same time, the replacement curve cam block 2 is provided with a second boss 21 at both axial ends. After the first boss 13 and the second boss 21 are combined, the outer end face is a cylindrical surface, and the locking ring 4 is locked on the cylindrical surface by threaded engagement. A matching groove that cooperates with the second boss 21 is provided on the first boss 13, so that the original cam block 1 and the replacement curve cam block 2 can be better assembled and convenient for fixing and locking the locking ring 4.

[0080] By rotating the locking ring 4, the internal threads 41 on the locking ring 4 engage with the external threads 31 on the first and second bosses 13, 21, allowing the locking ring 4 to move along the bosses toward the cam, preventing vertical separation between the original cam segment 1 and the replacement curved cam segment 2. After securing the locking ring 4 on one side, the same operation is performed to tighten the locking ring 4 on the other side. To facilitate rotational locking, four notches 42 are provided on the outer circumference of the locking ring 4. One end of the notches 42 is rounded to prevent stress concentration when the locking ring 4 is screwed in.

[0081] At the same time, the thickness of the positioning boss 11 is not less than half the thickness of the optimized cam 3 to ensure that the optimized cam 3 as a whole has sufficient bending strength. At the same time, the outer diameter of the positioning boss 11 is less than 2 / 3 of the maximum diameter of the original cam and greater than 1 / 2 of the sum of the maximum diameter and minimum diameter of the original cam to avoid the positioning groove 22 of the replacement curved cam block 2 being too large, resulting in the outer contour thickness of the replacement curved cam block 2 being too thin, and the optimized cam 3 having insufficient stiffness when in contact with the roller.

[0082] At the same time, the axial thickness of the first boss 13 must be no less than 1 / 2 of the difference between the outer diameter and the inner diameter of the roller to avoid the optimized cam 3 being too thin at the joint and damaging the thread. The outer diameter of the second boss 21 is equal to the outer diameter of the first boss 13 to ensure that the threads are on the same circumferential surface.

[0083] refer to Figure 12, the optimized cam 3 is assembled on the camshaft 6. The camshaft 6 is a stepped shaft. Both ends of the camshaft 6 are fixed in the camshaft 6 seat hole of the cam press. A flat keyway 7 is machined on the camshaft 6. The axial keyway 12 on the circumferential surface of the inner hole of the original cam block 1 is symmetrical about the cam rotation angle line of 0°. The centerline position of the axial keyway 12 is located at the starting point of the push stroke movement of the original cam block 1. At the same time, the position and direction of the flat keyway 7 are consistent with the axial block keyway to facilitate the optimization of the phase of the cam 3 when adjusting the starting position when installing the camshaft 6. The assembly of the optimized cam 3 first matches the positioning boss 11 of the original cam block 1 with the positioning groove 22 of the replacement curve block. After matching, a complete cam is formed. The cam is assembled on the camshaft 6 by the flat key 5. The end face of the boss at one end is against the step end face of the camshaft 6. The flat key 5 is used to fix it to avoid the cam from rotating during the subsequent thread matching.

[0084] The optimized cam 3 is used for a cam press with direct cam drive, so the cam needs to have a higher strength to meet the transmission of the punching force when the press is working. The original cam block 1, the replacement curve cam block 2 and the locking ring 4 are all made of Gcr15 steel and need to be tempered and heat treated so that the optimized cam 3 has sufficient strength.

[0085] The above are only preferred embodiments of the present invention and do not limit the implementation mode and protection scope of the present invention. For those skilled in the art, it should be aware that all solutions obtained by equivalent substitutions and obvious changes made using the contents of the present invention specification should be included in the protection scope of the present invention.

Claims

1. A cam optimization design method for a servo cam mechanical device, characterized in that: The steps include: Step 1: Draw the original cam profile after wear; Step 2: Draw the pressure angle-cam angle variation curve during the entire motion cycle of the original cam and the original displacement-cam angle curve of the follower in contact with the original cam high pair. The pressure angle is the angle between the follower motion direction and the normal direction of the contact point between the follower and the original cam. Step 3: Set the allowable pressure angle and record the cam angle range of the original cam whose pressure angle is greater than the allowable pressure angle during the entire motion cycle. This angle range is defined as the marked cam angle. Step 4: Based on the cam stroke corresponding to the marked cam angle, the original displacement of the follower corresponding to both ends of the marked cam angle, and the cam angle, combined with different follower motion laws, multiple replacement cam curve segments are obtained; Step 5: Draw the pressure angle-cam rotation angle curves of the various replacement cam curve segments obtained in step 4, select the replacement cam curve segments with a pressure angle not greater than the allowable pressure angle, and fit them to the cam profile outside the cam rotation angle range of the original cam mark; Step 6: Create replacement curve cam blocks based on the replacement cam curve segments fitted in step 5, and assemble the replacement curve cam blocks with the original cam blocks outside the marked cam angle range of the original cam to obtain an optimized cam; Wherein, in step 4, the motion law of the follower includes a linear polynomial motion law, a quadratic polynomial motion law, a quintic polynomial motion law, a cosine motion law, a sine motion law, and a motion law of a combination of two or more of the above motion laws; The motion equation of the follower is as follows: Linear polynomial motion law: s=C0+C1δ(1-1) Quadratic polynomial motion law: s=C0+C1δ+C2δ 2 (1-2) Cosine acceleration motion law: The equation of motion during the push stroke is: s = h[1-cos(πδ / δ0)] / 2 (1-3) The equation of motion during the return stroke is: s = h[1 + cos(πδ / δ′0)] / 2 (1-4) Sinusoidal acceleration motion law: The equation of motion during the push-pull process is: s = h[(δ / δ0)-sin(2πδ / δ0) / (2π)] (1-5) The equation of motion during the return stroke is: s = h[1-(δ / δ′0)+sin(2πδ / δ′0) / (2π)] (1-6) In the above formula 、 、 is the undetermined coefficient, is the displacement of the follower, is the cam angle, is the cam movement angle during the push stroke, and δ0′ is the cam movement angle during the return stroke.

2. The cam optimization design method for servo cam mechanical equipment according to claim 1, characterized in that: In step 1, the original cam profile is drawn based on the original cam structural parameters after wear and the original motion law of the follower in contact with the original cam high pair, wherein the cam structural parameters include the cam base circle radius, thrust motion angle, distal repose angle, return motion angle, proximal repose angle, maximum thrust displacement and cam speed.

3. The cam optimization design method for servo cam mechanical equipment according to claim 1, characterized in that: In step 5, if there are multiple replacement cam curve segments with a pressure angle not greater than the allowable pressure angle, the replacement cam curve segment with a smaller pressure angle is selected.

4. An optimized cam for a servo cam mechanical device, characterized in that: include: Original cam blocks and replacement curved cam blocks assembled into a complete cam, and locking rings for locking the original cam blocks and replacement curved cam blocks; The original cam block is provided with a first boss on both axial side walls, a positioning boss is provided on the original cam block at the position where it is assembled with the replacement curved cam block, a positioning groove that cooperates with the positioning boss is provided on the replacement curved cam block, and a second boss is provided on both axial ends of the replacement curved cam block. After the first boss and the second boss are combined, the outer end surface is a cylindrical surface, and the locking ring is locked on the cylindrical surface; The above-mentioned original cam blocks and replacement curve cam blocks are designed by the servo cam mechanical equipment cam optimization design method described in any one of claims 1 to 3.

5. The optimized cam of the servo cam mechanical device according to claim 4, characterized in that: The locking ring is locked on the first boss and the second boss through threaded engagement; a notch is provided on the locking ring for easy rotation and installation.

6. The optimized cam of the servo cam mechanical device according to claim 4, characterized in that: The first boss is provided with a matching groove which matches with the second boss.

7. The optimized cam of the servo cam mechanical device according to claim 4, characterized in that: The positioning boss is fan-shaped and is located in the middle of the original cam block in the axial direction.

8. The optimized cam of the servo cam mechanical device according to claim 7, characterized in that: The axial thickness of the positioning boss is not less than 1 / 2 of the thickness of the original cam block; the outer diameter of the positioning boss is less than 2 / 3 of the maximum diameter of the original cam block and greater than 1 / 2 of the sum of the maximum diameter and the minimum diameter of the original cam block.

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