A dual servo host
By using real-time position comparison and vibration cancellation technology with dual servo hosts, the problem of camshaft deflection in large-format hot stamping machines has been solved, achieving high-precision synchronous motion control and improving equipment safety, thus meeting the requirements of high-end hot stamping processes.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- GUANGDONG RUIBANG INTELLIGENT EQUIP TECH CO LTD
- Filing Date
- 2025-09-30
- Publication Date
- 2026-07-21
AI Technical Summary
The camshaft of current large-format hot stamping machines is deformed due to its excessive length-to-diameter ratio when running at high speed, resulting in uneven hot stamping pressure and failing to meet the requirements of high-end processes. Existing technology cannot effectively solve this problem.
It adopts a dual servo host, and through two independent camshafts and motor assemblies, it compares the position difference in real time, uses an absolute rotary encoder for precise synchronous control, and compensates for installation errors through a coupling to achieve efficient motion conversion and vibration cancellation.
It achieves high-precision synchronous motion control, prevents equipment collisions, improves equipment reliability and safety, reduces maintenance costs, and meets the precision and stability requirements of high-end hot stamping processes.
Smart Images
Figure CN224528249U_ABST
Abstract
Description
Technical Field
[0001] This utility model belongs to the field of motor technology, and specifically relates to a dual servo host. Background Technology
[0002] Hot stamping is a key process in the packaging and printing industry for enhancing product appearance and anti-counterfeiting features. With evolving market demands, hot stamping equipment is continuously expanding its width to meet the processing needs of large-format tobacco and alcohol packaging and luxury goods labels in mass production.
[0003] Currently, large-format hot stamping machines with a width of 1150mm or more generally employ a single camshaft to drive the hot stamping plate. However, as the length of the drive camshaft increases, when the length-to-diameter ratio (L / D) exceeds 20, it enters a rigidity dead zone, causing significant flexural deformation of the shaft. Specifically, under high-speed operation (greater than 8000 times / hour) and continuous high-pressure operation, the support stiffness in the middle of the single camshaft is severely insufficient, resulting in flexural deformation exceeding 0.15mm. This deformation directly causes the hot stamping plate fixed to the camshaft to tilt, disrupting the parallelism between the plate and the pressure platform, thus causing severe unevenness in hot stamping pressure across the entire surface. Specifically, the pressure is concentrated in the middle of the camshaft, while the pressure at both ends is insufficient, ultimately forming an unavoidable "false hot stamping" defect at the edges of wide-format materials. The sharpness of the lines cannot meet the requirements of high-end processes, with a typical error greater than -0.1mm to 0.1mm, significantly reducing the product yield.
[0004] Existing technologies attempt to alleviate the above problems by increasing the camshaft diameter, using higher strength materials, or optimizing the support structure. However, these methods are limited by the mechanical properties of materials and the spatial layout of equipment, and cannot fundamentally overcome the rigidity limit of the length-to-diameter ratio determined by physical laws. This restricts the technological path for large-format hot stamping equipment to develop towards higher precision and higher speed. Utility Model Content
[0005] To address the aforementioned problems, the primary objective of this invention is to provide a dual-servo host to solve the technical problem of significant flexural deformation of the camshaft caused by its excessively large length-to-diameter ratio.
[0006] To achieve the above objectives, the technical solution of this utility model is as follows:
[0007] This utility model provides a dual-servo host, including: a first drive assembly, including a first camshaft, a first motor disposed on the first camshaft, and a first detection unit, wherein the first detection unit is used to detect a first position of the first camshaft;
[0008] The second drive assembly includes a second camshaft, a second motor disposed on the second camshaft, and a second detection unit; the second detection unit is used to detect a second position of the second camshaft; the second camshaft is spaced apart from the first camshaft.
[0009] The controller is connected to the first motor, the second motor, the first detection unit, and the second detection unit respectively, and is used to compare the first position and the second position in real time. When the difference between the first position and the second position is greater than a preset safety threshold, it is determined that the host has malfunctioned.
[0010] This utility model provides a dual-servo host that, by comparing the first position of the first camshaft with the second position of the second camshaft in real time, ensures that the first and second camshafts maintain a precise phase relationship during high-speed operation. This is the foundation for achieving all subsequent accuracy and performance improvements. When the difference between the first and second positions exceeds a preset safety threshold, an anomaly can be detected in a timely manner, effectively preventing serious equipment collisions caused by slippage, wear, or breakage of mechanical transmission components such as couplings and / or reducers. This greatly improves the reliability and safety of the equipment, reduces potential huge maintenance costs and production downtime, and thus achieves high-precision synchronous motion control and inherent safety.
[0011] Furthermore, the first detection unit includes a first absolute rotary encoder; the second detection unit includes a second absolute rotary encoder.
[0012] Using a first absolute rotary encoder and a second absolute rotary encoder as detection units, no zero-return operation is required. The current position can be remembered after power failure and can be put into synchronization state immediately upon power-up, which improves the availability and ease of operation of the equipment and realizes absolute position feedback. In addition, it provides a high-resolution position signal, making the comparison and judgment of the controller more accurate and reliable, ensuring the accuracy of synchronization tolerance control, which is a prerequisite for realizing micron-level vibration control and high-precision synchronization, thereby realizing reliability detection.
[0013] Furthermore, the controller is configured to determine that the first camshaft and the second camshaft have lost synchronization when the difference between the feedback signals of the first absolute encoder and the second absolute encoder is greater than a preset synchronization tolerance, and adjust the output of the first motor or the second motor to resynchronize.
[0014] It can not only detect faults, but also actively intervene when slight loss of synchronization occurs, that is, when the dangerous threshold is not reached but the process quality is affected. By adjusting the motor output, it can resynchronize and achieve dynamic fault tolerance and self-adaptation. It ensures continuous high precision, so that the equipment can automatically maintain the highest process stability during long-term operation, resist minor disturbances caused by factors such as load changes and temperature drift, and ensure that the production yield is always high.
[0015] Furthermore, the first drive assembly further includes: a first coupling disposed between the first motor and the first camshaft; the second drive assembly further includes: a second coupling disposed between the second motor and the second camshaft.
[0016] By using a first coupling and a second coupling, alignment errors are compensated, allowing for minor installation errors between the first motor and the first camshaft, and between the second motor and the second camshaft, thus reducing manufacturing and assembly difficulties and costs. Furthermore, it achieves buffering and vibration reduction, specifically absorbing, to a certain extent, the impacts and vibrations during the start-up, shutdown, and high-speed operation of the first motor and / or the second motor, helping to protect the first motor, the second motor, and their corresponding transmission components, extending their service life, and simultaneously reducing overall vibration suppression to less than 8μm.
[0017] Furthermore, the first camshaft includes a first eccentric shaft and a first eccentric cam disposed on the first eccentric shaft; the second camshaft includes a second eccentric shaft and a second eccentric cam disposed on the second eccentric shaft; the first eccentric cam and the second eccentric cam are used to drive the hot stamping mechanism to move vertically.
[0018] The first eccentric cam converts the rotational motion of the first motor into the precise vertical reciprocating motion required for hot stamping, and the second eccentric cam converts the rotational motion of the second motor into the precise vertical reciprocating motion required for hot stamping. It is highly efficient and has sufficient structural rigidity, thus achieving high-efficiency motion conversion.
[0019] Furthermore, the first eccentric cam and the second eccentric cam are 0 degrees out of phase.
[0020] The design of a 0-degree phase difference between the first and second camshafts is key to achieving revolutionary vibration suppression. The centrifugal force of the first eccentric shaft moving upward cancels out the centrifugal force of the second eccentric shaft moving downward, or vice versa. This results in extremely smooth operation of the entire machine, with a resonance amplitude of less than 8μm. This allows for exceeding the speed limit of more than 6000 times per hour and significantly improves the sharpness of hot stamping lines, thus achieving mechanical balance.
[0021] Furthermore, the resonance amplitude of the first motor and the second motor is less than 8μm.
[0022] By limiting the resonance amplitude of the first and second motors to less than 8μm, a high level of vibration control was achieved, ensuring high-speed operation of the system and high-quality hot stamping.
[0023] Furthermore, the thermal expansion phase offset between the first camshaft and the second camshaft is compressed to less than or equal to 0.02 mm.
[0024] By limiting the thermal expansion phase offset between the first camshaft and the second camshaft to less than or equal to 0.02mm, the thermal stability of the equipment under long-term continuous 24-hour high-intensity production is ensured, and the precision degradation caused by temperature rise is avoided.
[0025] Furthermore, the flexural deformation of the first camshaft and the second camshaft is less than 0.03 mm.
[0026] By limiting the flexural deformation of the first and second camshafts to less than 0.03 mm, it is demonstrated that the structural enhancement of rigidity brought about by the first and second camshafts is the basis for ensuring uniform pressure across the entire width and parallelism of the printing plate.
[0027] Furthermore, the full-width pressure fluctuation of the first camshaft and the second camshaft is less than or equal to 4%.
[0028] By limiting the pressure fluctuation across the entire width of the first and second camshafts to less than or equal to 4%, the final process effect is fully realized, completely solving the problem of edge heat transfer in wide-width hot stamping and meeting the stringent requirements of high-end applications such as luxury packaging.
[0029] Compared with existing technologies, this application offers the following advantages: The dual-servo host, by comparing the first position of the first camshaft with the second position of the second camshaft in real time, ensures that the first and second camshafts maintain a precise phase relationship during high-speed operation, which is the foundation for all subsequent accuracy and performance improvements. When the difference between the first and second positions exceeds a preset safety threshold, an anomaly can be detected promptly, effectively preventing serious equipment collisions caused by slippage, wear, or breakage of mechanical transmission components. This greatly improves the reliability and safety of the equipment, reduces potential huge maintenance costs and production downtime, thereby achieving high-precision synchronous motion control and inherent safety. Attached Figure Description
[0030] Figure 1 This is a three-dimensional schematic diagram of the first drive component of a dual-servo host provided by this utility model.
[0031] Figure 2 This is a three-dimensional schematic diagram of the second drive component of a dual-servo host provided by this utility model.
[0032] In the figure: 10, first drive assembly; 11, first camshaft; 111, first eccentric shaft; 112, first eccentric cam; 12, first motor; 13, first detection unit; 14, first coupling; 20, second drive assembly; 21, second camshaft; 211, second eccentric shaft; 212, second eccentric cam; 22, second motor; 23, second detection unit; 24, second coupling. Detailed Implementation
[0033] To make the objectives, technical solutions, and advantages of this utility model clearer, the present utility model will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present utility model and are not intended to limit the present utility model.
[0034] It should be added that the current motors also have the following defects:
[0035] In the process of hot stamping equipment developing towards high speed and high precision, in addition to the limitations of structural rigidity, the inherent dynamic defects of the single camshaft drive system are another major technical bottleneck restricting its performance improvement. Specifically, under high-speed operation, such as at speeds exceeding 4000 times / hour, the enormous reciprocating mass generates extremely strong inertial forces and impact vibrations. The single camshaft and its drive system must bear all these periodic excitation forces alone, resulting in severe vibration of the entire machine, with a resonance amplitude exceeding 30μm. This vibration not only severely degrades the sharpness of the hot stamping lines, making fine patterns blurry, but is also the fundamental reason why the equipment cannot climb to higher speeds, such as 6000 times / hour. The severe vibration also causes transmission components such as bearings and gears to bear impact loads far exceeding design standards, leading to problems such as bearing overload of 200% and accelerated gear wear, significantly shortening the equipment's service life and maintenance cycle, and increasing production costs.
[0036] Existing technologies typically employ methods such as adding counterweights, optimizing cam curves, or reinforcing the frame to attempt to suppress vibration. However, these methods have limited effectiveness and often come at the cost of increased system inertia and energy consumption, failing to fundamentally balance and counteract the vibration source. Therefore, a fundamental contradiction exists between speed and stability in single-axis systems, making them unable to meet the stringent requirements of high-end applications for ultra-high-speed, stable mass production and ultra-long equipment lifespan. Ultra-high speed can be, for example, greater than 8000 cycles per hour.
[0037] It should be noted that for tobacco and alcohol packaging, continuous 24-hour production of gold cardboard or laser film is required, with a packaging rate exceeding 8000 times per hour. The rigidity of the cam mechanism must ensure the sharpness of the hot stamping lines, with an error margin of less than or equal to -0.1mm to 0.1mm. Furthermore, for luxury brand labels, dual-servo dynamic pressure adjustment is used to achieve simultaneous hot stamping of complex embossed textures, with a pressure accuracy of -2% to 2% to meet anti-counterfeiting requirements. Additionally, for precision processing of ultra-thin materials, in scenarios where the thickness of PET film or transfer electroplated aluminum is less than 0.05mm, a cam phase fine-tuning tolerance of -0.03° to 0.03° is necessary to prevent material stretching and deformation, ensuring a yield rate greater than 99.5%.
[0038] To achieve the above objectives, the technical solution of this utility model is as follows:
[0039] See Figure 1 and Figure 2 This utility model provides a dual-servo host, including: a first drive assembly 10, including a first camshaft 11, a first motor 12 disposed on the first camshaft 11, and a first detection unit 13, the first detection unit 13 being used to detect a first position of the first camshaft 11; a second drive assembly 20, including a second camshaft 21, a second motor 22 disposed on the second camshaft 21, and a second detection unit 23; the second detection unit 23 being used to detect a second position of the second camshaft 21; the second camshaft 21 being spaced apart from the first camshaft 11; and a controller, connected to the first motor 12, the second motor 22, the first detection unit 13, and the second detection unit 23 respectively, for comparing the first position and the second position in real time, and determining that the host has malfunctioned when the difference between the first position and the second position is greater than a preset safety threshold.
[0040] This utility model provides a dual-servo host that, by comparing the first position of the first camshaft 11 with the second position of the second camshaft 21 in real time, ensures that the first camshaft 11 and the second camshaft 21 maintain a precise phase relationship during high-speed operation. This is the foundation for achieving all subsequent accuracy and performance improvements. When the difference between the first and second positions exceeds a preset safety threshold, an anomaly can be detected in a timely manner, effectively preventing serious equipment collisions caused by slippage, wear, or breakage of mechanical transmission components such as couplings and / or reducers. This greatly improves the reliability and safety of the equipment, reduces potential huge maintenance costs and production downtime, and thus achieves high-precision synchronous motion control and inherent safety.
[0041] Furthermore, the first detection unit 13 includes a first absolute rotary encoder; the second detection unit 23 includes a second absolute rotary encoder.
[0042] Using a first absolute rotary encoder and a second absolute rotary encoder as detection units, no zero-return operation is required. The current position can be remembered after power failure and can be put into synchronization state immediately upon power-up, which improves the availability and ease of operation of the equipment and realizes absolute position feedback. In addition, it provides a high-resolution position signal, making the comparison and judgment of the controller more accurate and reliable, ensuring the accuracy of synchronization tolerance control, which is a prerequisite for realizing micron-level vibration control and high-precision synchronization, thereby realizing reliability detection.
[0043] Furthermore, the controller is used to determine that the first camshaft 11 and the second camshaft 21 have lost synchronization when the difference between the feedback signals of the first absolute encoder and the second absolute encoder is greater than the preset synchronization tolerance, and adjust the output of the first motor 12 or the second motor 22 to resynchronize.
[0044] This system not only detects faults but also proactively intervenes when slight loss of synchronization occurs—that is, when the dangerous threshold is not reached but the process quality is affected. It resynchronizes by adjusting the output of the first motor 12 and the second motor 22, achieving dynamic fault tolerance and self-adaptation. It ensures continuous high precision, enabling the equipment to automatically maintain the highest process stability during long-term operation, resisting minor disturbances caused by factors such as load changes and temperature drift, and ensuring that the production yield remains high.
[0045] Furthermore, the first drive assembly 10 further includes a first coupling 14 disposed between the first motor 12 and the first camshaft 11; the second drive assembly 20 further includes a second coupling 24 disposed between the second motor 22 and the second camshaft 21.
[0046] By using the first coupling 14 and the second coupling 24, alignment errors are compensated, allowing for minor installation errors between the first motor 12 and the first camshaft 11, and between the second motor 22 and the second camshaft 21, reducing manufacturing and assembly difficulties and costs. Furthermore, it achieves buffering and vibration reduction, specifically absorbing shocks and vibrations during the start-up, shutdown, and high-speed operation of the first motor 12 and / or the second motor 22 to a certain extent, helping to protect the first motor 12, the second motor 22, and their corresponding transmission components, extending their service life, and simultaneously reducing overall vibration suppression to less than 8μm.
[0047] Furthermore, the first camshaft 11 includes a first eccentric shaft 111 and a first eccentric cam 112 disposed on the first eccentric shaft 111; the second camshaft 21 includes a second eccentric shaft 211 and a second eccentric cam 212 disposed on the second eccentric shaft 211; the first eccentric cam 112 and the second eccentric cam 212 are used to drive the hot stamping mechanism to move vertically.
[0048] The first eccentric cam 112 converts the rotational motion of the first motor 12 into the precise vertical reciprocating motion required for hot stamping, and the second eccentric cam 212 converts the rotational motion of the second motor 22 into the precise vertical reciprocating motion required for hot stamping. It is highly efficient and has sufficient structural rigidity, thus achieving high-efficiency motion conversion.
[0049] Furthermore, the first eccentric cam 112 and the second eccentric cam 212 are 0 degrees out of phase.
[0050] The design of the first camshaft 11 and the second camshaft 21 having a 0-degree phase difference ensures that the first eccentric cam 112 and the second eccentric cam 212 move synchronously, reaching their high points or low points simultaneously, which is key to achieving revolutionary vibration suppression. The centrifugal force of the first eccentric shaft 111 moving upward cancels out the centrifugal force of the second eccentric shaft 211 moving downward, or vice versa, making the entire machine run extremely smoothly. The resonance amplitude of the two is less than 8μm, thus allowing the speed limit to be exceeded, specifically greater than 6000 times / hour, and significantly improving the sharpness of the hot stamping lines to achieve mechanical balance.
[0051] Furthermore, the resonance amplitude of the first motor 12 and the second motor 22 is less than 8μm.
[0052] Compared to the single-axis limit of 5000 cycles, the dual-axis centrifugal force balance of the first camshaft 21 and the second camshaft 22, i.e., the mutual cancellation of the centrifugal force, allows for high-speed operation exceeding 6000 cycles / hour, achieving a breakthrough in speed limits and increasing production capacity by 20%. Compared to the single-axis resonance amplitude of greater than 15μm, the dual servo host can implement an anti-phase vibration cancellation algorithm to achieve a resonance amplitude of less than 8μm. By limiting the resonance amplitude of the first motor 12 and the second motor 22 to less than 8μm, a high level of vibration control is clearly defined, ensuring high-speed operation of the system and high-quality hot stamping, and improving the sharpness of hot stamping lines by 40%.
[0053] Furthermore, the thermal expansion phase offset between the first camshaft 21 and the second camshaft 22 is compressed to less than or equal to 0.02 mm.
[0054] Compared to a single-axis thermal expansion offset greater than or equal to 0.05 mm and a single-axis body temperature rise greater than 80 °C, by distributing heat to the first camshaft 21 and the second camshaft 22, the temperature rise of the dual-axis body is less than 60 °C, and the dual-axis thermal expansion phase offset is controlled within 0.02 mm. By limiting the dual-axis thermal expansion phase offset of the first camshaft 21 and the second camshaft 22 to less than or equal to 0.02 mm, the thermal stability of the equipment under long-term continuous 24-hour high-intensity production is ensured, avoiding precision degradation or thermal deformation caused by temperature rise and precisely suppressing it.
[0055] Furthermore, the flexural deformation of the first camshaft 21 and the second camshaft 22 is less than 0.03 mm.
[0056] Compared to the single-axis flexural deformation of 0.05mm for the first camshaft 21 or the second camshaft 22, the distance between the dual-axis support points of the first camshaft 21 and the second camshaft 22 is shortened by 60%, and the flexural deformation is less than 0.03mm. This ensures that the parallelism error of the hot stamping plate is 0.005mm / m to 0.005mm / m, and the parallelism accuracy of the plate is improved by 3 times. By limiting the flexural deformation of the first camshaft 21 and the second camshaft 22 to less than 0.03mm, it is proven that the structural enhancement of rigidity brought about by the first camshaft 21 and the second camshaft 22 is the basis for ensuring uniform pressure across the entire surface and the parallelism of the plate.
[0057] Furthermore, the full-width pressure fluctuation of the first camshaft 21 and the second camshaft 22 is less than or equal to 4%.
[0058] Compared to the approximately 8% pressure fluctuation across the entire width when using a single-axis solution with either the first camshaft 21 or the second camshaft 22, the dual-axis segmented pressure application with each camshaft 21 and 22 controlling a width of 575mm results in a pressure fluctuation of less than or equal to 4% across the entire width, completely eliminating edge heat transfer defects. By limiting the pressure fluctuation of the first camshaft 21 and the second camshaft 22 to less than or equal to 4% across the entire width, the problem of edge heat transfer in wide-width hot stamping is completely solved, meeting the stringent requirements of high-end applications such as luxury packaging. This enables simultaneous hot stamping of complex embossed textures with a pressure accuracy of -2% to 2%, ensuring anti-counterfeiting process requirements.
[0059] Furthermore, compared to the approximately 20,000-hour lifespan of a single axis, the dual-axis load splitting using the first camshaft 21 and the second camshaft 22 reduces bearing load by 50%, extending bearing life to over 30,000 hours, effectively doubling bearing life. A damaged single axis can be replaced independently. While single-axis maintenance and replacement requires 20 hours, dual-axis maintenance and replacement requires only 8 hours, reducing downtime by 60% and thus optimizing maintenance costs. The mechanical efficiency of a single axis is approximately 90%, while the mechanical efficiency of the dual-servo collaborative drive exceeds 93%, achieving a 15% reduction in energy consumption per ton of output, thereby improving energy efficiency.
[0060] This utility model provides a dual-servo host that, by comparing the first position of the first camshaft 21 with the second position of the second camshaft 22 in real time, ensures that the first camshaft 21 and the second camshaft 22 maintain a precise phase relationship during high-speed operation, which is the foundation for all subsequent accuracy and performance improvements. When the difference between the first and second positions exceeds a preset safety threshold, an anomaly can be detected in a timely manner, effectively preventing serious equipment collisions caused by slippage, wear, or breakage of mechanical transmission components. This greatly improves the reliability and safety of the equipment, reduces potential huge maintenance costs and production downtime, and thus achieves high-precision synchronous motion control and inherent safety. Therefore, by using a dual-axis design with the first camshaft 21 and the second camshaft 22, and through physical width division and mechanical coupling, the 1150mm width is transformed into two 575mm mature technology ranges, breaking through the rigid dead zone when the length-to-diameter ratio (L / D) of a single axis is greater than 20. This solves the problem that a single-axis solution with either the first camshaft 21 or the second camshaft 22 cannot meet the accuracy and reliability requirements of high-end hot stamping processes in terms of technical logic.
[0061] The above are merely preferred embodiments of the present utility model and are not intended to limit the present utility model. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.
Claims
1. A dual-servo host, characterized in that, include: The first drive assembly includes a first camshaft, a first motor disposed on the first camshaft, and a first detection unit, wherein the first detection unit is used to detect a first position of the first camshaft. The second drive assembly includes a second camshaft, a second motor disposed on the second camshaft, and a second detection unit; the second detection unit is used to detect a second position of the second camshaft; the second camshaft is spaced apart from the first camshaft. The controller is connected to the first motor, the second motor, the first detection unit, and the second detection unit respectively, and is used to compare the first position and the second position in real time. When the difference between the first position and the second position is greater than a preset safety threshold, it is determined that the host has malfunctioned.
2. A dual-server host as described in claim 1, characterized in that, The first detection unit includes a first absolute rotary encoder; The second detection unit includes a second absolute rotary encoder.
3. A dual-server host as described in claim 2, characterized in that, The controller is used to determine that the first camshaft and the second camshaft have lost synchronization when the difference between the feedback signals of the first absolute rotary encoder and the second absolute rotary encoder is greater than a preset synchronization tolerance, and to adjust the output of the first motor or the second motor to resynchronize.
4. A dual-server host as described in claim 1, characterized in that, The first drive assembly further includes: a first coupling disposed between the first motor and the first camshaft; The second drive assembly further includes a second coupling disposed between the second motor and the second camshaft.
5. A dual-servo host as described in claim 1, characterized in that, The first camshaft includes a first eccentric shaft and a first eccentric cam disposed on the first eccentric shaft; the second camshaft includes a second eccentric shaft and a second eccentric cam disposed on the second eccentric shaft. The first eccentric cam and the second eccentric cam are used to drive the hot stamping mechanism to move vertically.
6. A dual-servo host as described in claim 5, characterized in that, The first eccentric cam and the second eccentric cam are 0 degrees out of phase.
7. A dual-server host as described in claim 1, characterized in that, The resonance amplitude of the first motor and the second motor is less than 8μm.
8. A dual-server host as described in claim 1, characterized in that, The thermal expansion phase offset between the first camshaft and the second camshaft is compressed to less than or equal to 0.02 mm.
9. A dual-server host as described in claim 1, characterized in that, The flexural deformation of the first camshaft and the second camshaft is less than 0.03 mm.
10. A dual-server host as described in claim 1, characterized in that, The full-width pressure fluctuation of the first camshaft and the second camshaft is less than or equal to 4%.