Linkage discharging device

Abstract

The utility model relates to a linkage discharging device which comprises a machine table, a driving unit, a rotary supporting unit, a linkage adjusting unit and a transmission assembly. The rotary supporting unit comprises a first discharging pipe and a second discharging pipe which are arranged in parallel in a spaced mode, and the first discharging pipe and the second discharging pipe are rotationally arranged on the machine table through bearing assemblies. The linkage adjusting unit is provided with an expansion part capable of expanding in the radial direction. The transmission assembly comprises a driving gear connected with an output shaft of the driving motor, a first linkage gear and a second linkage gear, the first linkage gear and the second linkage gear are meshed with the driving gear, the first linkage gear is meshed with the first discharging pipe and the second discharging pipe and can drive the first discharging pipe and the second discharging pipe to rotate at the same time, and the second linkage gear is meshed with the linkage adjusting unit. The utility model provides a linkage discharging device to solve the problems that an existing printer discharging device is difficult to adapt to different materials, unstable in discharging, high in equipment complexity, large in energy consumption, high in maintenance cost and the like, and therefore the printing quality and the overall performance of a printer are improved.

Description

Technical Field

[0001] This utility model relates to the field of printer auxiliary equipment technology, specifically to a linkage feeding device for printers. Background Technology

[0002] In the printing process, the feeding of rolls of paper and other materials is crucial. Existing feeding devices for printers have several problems. On the one hand, different types and sizes of printers have varying requirements for paper size, weight, and material, and existing feeding devices often struggle to flexibly adapt to these diverse needs. For example, with thin thermal paper or easily deformable specialty paper, traditional feeding devices are prone to causing scratches and wrinkles on the paper surface due to forced feeding, affecting print quality. On the other hand, for heavy paper jams or thick paper rolls, existing feeding devices cannot precisely control the feeding tension, leading to uneven paper delivery and consequently affecting printing accuracy and consistency.

[0003] Furthermore, traditional feeding devices are structurally complex, with insufficient coordination between multiple transmission components. This not only increases energy consumption but also makes them prone to malfunctions, resulting in higher repair and maintenance costs. Moreover, during the feeding process, the lack of effective shock absorption and stabilization mechanisms allows vibrations generated by the rotating paper to be transmitted to the printer body, affecting overall stability and printing accuracy. Therefore, there is an urgent need for a new type of linked feeding device suitable for printers to solve these problems. Utility Model Content

[0004] In view of this, the present invention provides a linkage feeding device to solve the problems of existing printer feeding devices, such as difficulty in adapting to different materials, unstable feeding, high equipment complexity, high energy consumption and high maintenance costs, thereby improving the printing quality and overall performance of the printer.

[0005] The objective of this utility model is achieved through the following technical solution:

[0006] A linkage feeding device includes a machine base, a drive unit, a rotary support unit, a linkage adjustment unit, and a transmission assembly. The drive unit includes a drive motor mounted on the machine base. The rotary support unit includes a first feeding pipe and a second feeding pipe arranged in parallel and spaced apart, both of which are rotatably mounted on the machine base via bearing assemblies. The linkage adjustment unit has a radially expandable tightening portion. The transmission assembly includes a drive gear connected to the output shaft of the drive motor, a first linkage gear, and a second linkage gear, both meshing with the drive gear. The first linkage gear meshes with the first and second feeding pipes and can simultaneously drive both to rotate. The second linkage gear meshes with the linkage adjustment unit. The device has two operating modes: In the first operating mode, the first and second feeding pipes form a V-shaped support structure. The weight of the rolled material and the static friction between the two feeding pipes create a torque balance. When the first and second feeding pipes rotate, the rolled material rotates synchronously in opposite directions under the drive of static friction, thus achieving feeding. At this time, the tightening part maintains a radially expanded state and provides elastic constraint to the rolled material. In the second operating mode, the linkage adjustment unit is driven by the second linkage gear to generate rotational motion. Its tightening part expands radially and forms an interference fit with the inner wall of the rolled material. The active rotation of the linkage adjustment unit drives the rolled material to feed. The tightening part can expand radially to contact the inner wall of the rolled material.

[0007] By integrating the drive unit, rotating support unit, and linkage adjustment unit, flexible adaptation to roll materials of different sizes and weights is achieved. The first working mode utilizes the torque balance formed by the V-shaped support structure and static friction, enabling passive material feeding without complex control. This mode is suitable for printers using thin or easily deformable paper, such as thermal paper and thin coated paper, avoiding damage to the paper surface caused by forced driving and ensuring unaffected print quality. The second working mode uses the active expansion of the tensioning part to form an interference fit, precisely controlling the feeding tension of heavy roll materials to meet high-precision processing requirements. It is mainly used for printers handling heavy roll materials, such as thick cardstock and heavy coated paper, ensuring precise control of feeding tension and smooth paper delivery to the printer. Switching between the two modes is simply a matter of changing the placement position of the roll material, requiring no additional power source, significantly reducing equipment complexity and energy consumption. The triangular spatial layout creates a stable mechanical distribution between the transmission system and the support structure, effectively absorbing radial vibration during material rotation and extending the service life of the bearing components. The elastic constraint design allows for slight displacement deviations in the material while ensuring the frictional driving force, preventing jamming caused by material eccentricity.

[0008] Preferably, the first linkage gear and the second linkage gear are located on opposite sides of the driving gear.

[0009] The symmetrically arranged linkage gear system on both sides of the driving gear forms a bidirectional power output topology. This layout minimizes the power transmission path, significantly reduces energy loss during gear meshing, and improves transmission efficiency. The symmetrical meshing forces of the gears on both sides can cancel each other out radial loads, greatly reducing bending stress on the driving gear shaft and extending the service life of the drive motor. The special opposite-side arrangement naturally makes the rotation directions of the two linkage gears complementary, providing a natural phase difference basis for the coordinated control of different functional modules. This spatial layout also facilitates modular maintenance; when a single gear is damaged, it can be disassembled and replaced independently without affecting the overall structure, significantly reducing maintenance costs. From a thermodynamic perspective, the symmetrical distribution helps to evenly distribute the heat generated by gear meshing, avoiding lubricant failure caused by localized overheating.

[0010] Preferably, the first discharge pipe is equipped with a first driven gear, the second discharge pipe is equipped with a second driven gear, and the first linkage gear simultaneously meshes with the first driven gear and the second driven gear.

[0011] The dual driven gear synchronous meshing design creatively solves the phase synchronization problem of traditional dual-shaft drive systems. By simultaneously driving two driven gears with a single linkage gear, the speed difference between the two feed tubes is fundamentally eliminated, ensuring the symmetry of the V-shaped support structure remains stable. This design effectively controls the angular displacement error of the two feed tubes, preventing material slippage caused by asynchronous speeds. The direct connection between the driven gears and the feed tubes eliminates the need for traditional chain or belt drives, reducing the cumulative error of elastic deformation in the transmission system. The modular gear set design allows for quick replacement of gear sets with different modules according to material weight, expanding the equipment's load capacity range. The preload generated by the precision gear meshing also automatically compensates for bearing clearance, ensuring transmission accuracy stability after long-term use.

[0012] Preferably, the outer periphery of the tightening part is provided with an array of friction protrusions. The linkage adjustment unit is provided with a linkage driven gear, which meshes with the second linkage gear for transmission.

[0013] The innovative friction protrusion array employs biomimetic design principles, mimicking the microstructure of reptile skin. Each protrusion unit is distributed in a multi-level pyramid shape, achieving adaptive distribution of contact pressure through a gradient hardness composite layer. When the expansion portion radially expands, the protrusion array undergoes graded deformation: primary protrusions provide basic frictional force, while secondary protrusions gradually participate in contact as pressure increases, forming nonlinear frictional characteristics. This design causes the coefficient of friction to exhibit a rapid initially increasing and then slowing growth curve with increasing pressure, ensuring both rapid response to initial contact and avoiding damage to the inner wall of the material caused by overpressure. The microtexture of the protrusion surface can also store lubricating medium, forming a microhydrodynamic effect during high-speed rotation, reducing the temperature rise of the contact surface. The array layout has excellent anti-fouling capabilities; debris can be naturally discharged along the gaps between the protrusions, avoiding the defects of traditional friction surfaces that are prone to fouling.

[0014] Preferably, in the first working mode, the rotation axis of the tightening part forms a triangular spatial layout with the rotation axes of the first discharge pipe and the second discharge pipe.

[0015] The triangular spatial layout creatively applies the principles of planar mechanics, with three rotational axes forming a stable kinematic constraint system. This layout ensures that the principal axes of the inertial tensors of each moving component form optimal angles in space, effectively reducing dynamic imbalances during high-speed rotation. From a dynamic perspective, the triangular layout decomposes the centrifugal force of the rotating components into three mutually constraining components, significantly reducing the vibration amplitude of the machine's foundation structure. The spatial geometry also ensures that the tightening section and the discharge pipe form the optimal angle of action, allowing for a smooth transition in the material's trajectory when switching between the two operating modes.

[0016] Preferably, the machine base includes two parallel upright plates, and the drive motor is fixedly installed on the back of the upright plates.

[0017] The double-plate structure utilizes the box girder design concept from bridge engineering, forming a closed torsional section. Multiple transverse stiffeners connect the parallel plates, creating a high-rigidity, low-weight composite frame structure. This design ensures the machine's natural frequency avoids the common operating frequency range, effectively suppressing resonance. The rear-mounting method of the plates shifts the center of gravity of the drive unit backward, increasing the overall anti-overturning moment and improving operational stability. Stress diffusion grooves on the plate surfaces evenly distribute concentrated loads to the foundation, preventing localized plastic deformation.

[0018] Preferably, it also includes a protective cover covering the outside of the drive gear, the first linkage gear and the second linkage gear.

[0019] The integrated protective cover employs a fluid-structure interaction noise reduction design, featuring an internal Helmholtz resonant cavity array. Each cavity is tuned to absorb the main frequency noise of gear meshing, thereby reducing equipment operating noise. The curved shape of the protective cover has been optimized through computational fluid dynamics to create airflow channels that facilitate heat dissipation while preventing the intrusion of external dust.

[0020] Preferably, the outer surfaces of the first and second discharge pipes are provided with axially extending anti-slip stripes, and the stripe cross-section is a trapezoidal protrusion.

[0021] The trapezoidal cross-section anti-slip stripes integrate the principles of tribology and materials mechanics, with optimized stripe angles. When material contacts the discharge pipe, the trapezoidal slope generates a normal component force, increasing the effective contact pressure, while the flat-top structure prevents stress concentration and damage to the material surface. The gradient design of the stripe depth creates a gradual distribution of the friction coefficient along the axial direction, effectively suppressing axial movement of the material.

[0022] Preferably, the rotating support unit has symmetrical limiting retaining rings at both ends, and the retaining rings are fixed to the end of the feeding tube by set screws.

[0023] The adjustable limit retaining ring system adopts a split design concept, separating the retaining ring body from the locking function module. The symmetrical arrangement of the two retaining rings forms a dynamic balance constraint system, which can adaptively compensate for the axial dimensional tolerances of the material roll. The elastic gasket on the inner surface of the retaining ring is made of shape memory alloy material, which automatically adjusts the preload force when the temperature changes. The three-dimensional curved contact surface design makes the contact stress distribution between the retaining ring and the material end face more uniform, avoiding the edge stress concentration caused by traditional flat retaining rings.

[0024] The advantages of this utility model compared to the prior art are:

[0025] By integrating the drive unit, the rotating support unit, and the linkage adjustment unit, the printer achieves flexible adaptation to roll materials of different sizes, weights, and materials, meeting the diverse paper requirements of the printer and improving its versatility and applicability.

[0026] The first operating mode utilizes the torque balance created by the V-shaped support structure and static friction to achieve passive feeding of thin or easily deformable paper without complex control, avoiding damage to the paper surface caused by forced driving and ensuring that print quality is not affected. The second operating mode uses the active expansion of the tensioning part to form an interference fit, which can precisely control the feeding tension of heavy rolls, ensuring that the paper is smoothly fed into the printer for printing, meeting the feeding requirements of different types of paper. Switching between the two modes can be completed simply by changing the gear transmission path, without the need for an additional power source, significantly reducing equipment complexity and energy consumption, and meeting the requirements of energy-saving and high-efficiency operation of printers.

[0027] The design of symmetrically arranged linkage gears on both sides of the drive gear minimizes the power transmission path, improves transmission efficiency, reduces energy consumption of the drive motor, extends the service life of the drive motor, and reduces printer maintenance costs. It also provides a phase difference basis for collaborative control, facilitates modular maintenance, reduces maintenance costs, minimizes printer downtime due to material feeding device failure, and improves printer efficiency.

[0028] The dual driven gear synchronous meshing design solves the phase synchronization problem of traditional dual-axis drive systems, ensures the stability of the V-shaped support structure, controls angular displacement error, reduces transmission link error, expands the load capacity range of the equipment, and ensures transmission accuracy and stability. This makes the paper feeding process of the printer more accurate and stable, which is conducive to improving print quality.

[0029] The array of friction protrusions on the outer periphery of the tensioning part has non-linear friction characteristics, which can protect the inner wall of the paper, reduce the temperature rise of the contact surface, and has anti-contamination ability, ensuring that the quality of the paper is not affected during the feeding process and improving the printing effect of the printer.

[0030] The triangular spatial layout reduces dynamic imbalance, decreases machine vibration amplitude, ensures a smooth transition of paper movement trajectory when switching working modes, improves the overall stability of the printer and the continuity of the feeding process, and helps the printer achieve high-quality and high-efficiency printing.

[0031] The double-plate structure suppresses resonance, improves equipment stability, avoids local plastic deformation, extends the service life of the machine and feeding device, and reduces the overall maintenance cost of the printer.

[0032] The protective cover reduces equipment operating noise, facilitates heat dissipation, prevents external dust from entering, ensures the normal operation of transmission components, extends the service life of gears and other parts, and improves the reliability and stability of the printer's feeding device.

[0033] The trapezoidal cross-section anti-slip stripes increase effective contact pressure, prevent stress concentration, suppress axial movement of the paper, and ensure the accuracy of the paper's position during the feeding process, which is beneficial for the printer to achieve precise printing.

[0034] The adjustable limit ring system adaptively compensates for the axial dimensional tolerance of the paper roll, resulting in a more uniform distribution of contact stress, preventing damage to the paper end face, ensuring the integrity of the paper, and thus improving the printer's print quality. Attached Figure Description

[0035] To more clearly illustrate the technical solutions of the embodiments of this application, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of this application and should not be regarded as a limitation of the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0036] Figure 1 This is a structural diagram of a linkage feeding device according to an embodiment of the present invention.

[0037] Figure 2 This is a schematic diagram of the linkage feeding device in the first working mode according to an embodiment of the present invention.

[0038] Figure 3 This is a schematic diagram of the linkage feeding device in the second working mode according to an embodiment of the present invention.

[0039] Figure 4 This is a three-dimensional structural diagram of a linkage feeding device according to an embodiment of the present invention.

[0040] Figure 5 This is a partial three-dimensional structural diagram of a linkage feeding device according to an embodiment of the present invention.

[0041] Label description: machine base (1), upright plate (11), drive unit (2), drive motor (21), rotating support unit (3), first feeding pipe (31), first driven gear (311), second feeding pipe (32), second driven gear (321), linkage adjustment unit (4), tensioning part (41), linkage driven gear (42), transmission assembly (5), drive gear (51), first linkage gear (52), second linkage gear (53), protective cover (6), rolled material (01). Detailed Implementation

[0042] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. The components of the embodiments of this application described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0043] Therefore, the following detailed description of the embodiments of this application provided in the accompanying drawings is not intended to limit the scope of the claimed application, but merely to illustrate selected embodiments of the application. All other embodiments obtained by those skilled in the art based on the embodiments of this application without inventive effort are within the scope of protection of this application.

[0044] It should be noted that similar reference numerals and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures. In the description of the embodiments of this application, it should be understood that the terms "upper," "lower," "left," "right," "vertical," "horizontal," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the figures, or the orientation or positional relationship commonly used when the product of this application is in use, or the orientation or positional relationship commonly understood by those skilled in the art. 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.

[0045] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other.

[0046] The technical solutions in this application will now be described with reference to the accompanying drawings.

[0047] This embodiment provides a linkage feeding device, including a machine base 1, a drive unit 2, a rotary support unit 3, a linkage adjustment unit 4, and a transmission assembly 5. The drive unit 2 includes a drive motor 21 mounted on the machine base 1. The rotary support unit 3 includes a first feeding pipe 31 and a second feeding pipe 32 arranged in parallel and spaced apart, both of which are rotatably mounted on the machine base 1 via bearing assemblies. The linkage adjustment unit 4 has a radially expandable tightening part 41. The transmission assembly 5 includes a drive gear 51 connected to the output shaft of the drive motor 21, a first linkage gear 52 and a second linkage gear 53 both meshing with the drive gear 51. The first linkage gear 52 meshes with the first feeding pipe 31 and the second feeding pipe 32 and can simultaneously drive both of them to rotate. The second linkage gear 53 meshes with the first feeding pipe 31 and the second feeding pipe 32 and can simultaneously drive both of them to rotate. The dynamic adjustment unit 4 is engaged; the device has two working modes: In the first working mode, the first discharge pipe 31 and the second discharge pipe 32 form a V-shaped support structure. The torque balance is formed by the weight of the rolled material 01 and the static friction between the two discharge pipes. When the first discharge pipe 31 and the second discharge pipe 32 rotate, the rolled material 01 rotates synchronously in the opposite direction under the drive of static friction to realize the discharge. At this time, the tensioning part 41 maintains a radial expansion state and forms an elastic constraint on the rolled material 01. In the second working mode, the linkage adjustment unit 4 is driven by the second linkage gear 53 to generate a rotational motion. Its tensioning part 41 expands radially and forms an interference fit with the inner wall of the rolled material 01. The active rotation of the linkage adjustment unit 4 drives the rolled material 01 to discharge.

[0048] Through the synergistic action of the integrated drive unit 2, rotating support unit 3, and linkage adjustment unit 4, flexible adaptation to roll materials 01 of different sizes and weights is achieved. The first working mode utilizes the torque balance formed by the V-shaped support structure and static friction, enabling passive material feeding without complex control. This is particularly suitable for thin or easily deformable materials, avoiding surface damage caused by forced drive. The second working mode uses the active expansion of the tensioning part 41 to form an interference fit, precisely controlling the feeding tension of heavy roll materials to meet high-precision processing requirements. Switching between the two modes only requires changing the placement position of the roll material, eliminating the need for an additional power source and significantly reducing equipment complexity and energy consumption. The triangular spatial layout creates a stable mechanical distribution between the transmission system and the support structure, effectively absorbing radial vibration during material rotation and extending the service life of the bearing components. The elastic constraint design, while ensuring frictional driving force, allows for slight displacement deviations in the material, preventing jamming caused by material eccentricity.

[0049] In this embodiment, the first linkage gear 52 and the second linkage gear 53 are located on opposite sides of the driving gear 51, respectively.

[0050] The symmetrically arranged linkage gear system on both sides of the drive gear 51 forms a bidirectional power output topology. This layout minimizes the power transmission path, significantly reduces energy loss during gear meshing, and improves transmission efficiency. The symmetrical meshing forces of the gears on both sides can cancel each other out radial loads, greatly reducing bending stress on the shaft of the drive gear 51 and extending the service life of the drive motor 21. The special opposite-side arrangement naturally makes the rotation directions of the two linkage gears complementary, providing a natural phase difference basis for the coordinated control of different functional modules. This spatial layout also facilitates modular maintenance; when a single gear is damaged, it can be disassembled and replaced independently without affecting the overall structure, significantly reducing maintenance costs. From a thermodynamic perspective, the symmetrical distribution helps to evenly distribute the heat generated by gear meshing, avoiding lubricant failure caused by localized overheating.

[0051] In this embodiment, the first discharge pipe 31 is equipped with a first driven gear 311, the second discharge pipe 32 is equipped with a second driven gear 321, and the first linkage gear 52 simultaneously meshes with the first driven gear 311 and the second driven gear 321.

[0052] The dual driven gear synchronous meshing design creatively solves the phase synchronization problem of traditional dual-shaft drive systems. By simultaneously driving two driven gears with a single linkage gear, the speed difference between the two feed tubes is fundamentally eliminated, ensuring the symmetry of the V-shaped support structure remains stable. This design effectively controls the angular displacement error of the two feed tubes, preventing material slippage caused by asynchronous speeds. The direct connection between the driven gears and the feed tubes eliminates the need for traditional chain or belt drives, reducing the cumulative error of elastic deformation in the transmission system. The modular gear set design allows for quick replacement of gear sets with different modules according to material weight, expanding the equipment's load capacity range. The preload generated by the precision gear meshing also automatically compensates for bearing clearance, ensuring transmission accuracy stability after long-term use.

[0053] In this embodiment, the outer periphery of the tensioning part 41 is provided with an array of friction protrusions. The linkage adjustment unit 4 is provided with a linkage driven gear 42, which meshes with the second linkage gear 53 for transmission.

[0054] The innovative friction protrusion array employs biomimetic design principles, mimicking the microstructure of reptile skin. Each protrusion unit is distributed in a multi-level pyramid shape, achieving adaptive distribution of contact pressure through a gradient hardness composite material layer. When the expansion section 41 expands radially, the protrusion array undergoes graded deformation: primary protrusions provide basic frictional force, while secondary protrusions gradually participate in contact as pressure increases, forming nonlinear frictional characteristics. This design causes the coefficient of friction to exhibit a rapid-then-slow growth curve with increasing pressure, ensuring both rapid response to initial contact and avoiding damage to the inner wall of the material caused by overpressure. The microtexture of the protrusion surface can also store lubricating medium, forming a microhydrodynamic pressure effect during high-speed rotation, reducing the temperature rise of the contact surface. The array layout has excellent anti-fouling capabilities; debris can be naturally discharged along the gaps between the protrusions, avoiding the defects of traditional friction surfaces that are prone to fouling.

[0055] In this embodiment, in the first working mode, the rotation axis of the tensioning part forms a triangular spatial layout with the rotation axes of the first discharge pipe 31 and the second discharge pipe 32.

[0056] The triangular spatial layout creatively applies the principles of planar mechanics, with the three rotational axes forming a stable kinematic constraint system. This layout ensures that the principal axes of the inertial tensors of each moving component form an optimal angle in space, effectively reducing dynamic imbalance during high-speed rotation. From a dynamic perspective, the triangular layout decomposes the centrifugal force of the rotating components into three mutually constraining components, significantly reducing the vibration amplitude of the machine base structure 1. The spatial geometry also ensures that the tensioning part 41 forms an optimal angle with the discharge pipe, allowing for a smooth transition in the material's trajectory when switching between the two working modes.

[0057] In this embodiment, the machine base 1 includes two parallel upright plates 11, and the drive motor 21 is fixedly installed on the back of the upright plates 11.

[0058] The double-plate 11 structure applies the box girder design concept from bridge engineering, forming a closed torsional section. The parallel plates 11 are connected by multiple transverse stiffeners, constructing a high-rigidity, low-weight composite frame structure. This design ensures that the natural frequency of the machine platform 1 avoids the common operating frequency range, effectively suppressing resonance. The rear-mounting method of the plates 11 shifts the center of gravity of the drive unit 2 rearward, increasing the overall anti-overturning moment of the equipment and improving operational stability. The stress diffusion groove design on the surface of the plates 11 evenly transfers concentrated loads to the foundation, avoiding localized plastic deformation.

[0059] In this embodiment, a protective cover 6 is also included, which covers the outside of the drive gear 51, the first linkage gear 52 and the second linkage gear 53.

[0060] The integrated protective cover 6 employs a fluid-structure interaction noise reduction design, featuring an internal Helmholtz resonant cavity array. Each cavity is tuned to absorb the main frequency noise of gear meshing, thereby reducing equipment operating noise. The curved shape of the protective cover 6 has been optimized through computational fluid dynamics to create airflow channels that facilitate heat dissipation while preventing external dust intrusion.

[0061] In this embodiment, the outer surfaces of the first discharge pipe 31 and the second discharge pipe 32 are provided with axially extending anti-slip stripes, and the stripe cross-section is a trapezoidal protrusion.

[0062] The trapezoidal cross-section anti-slip stripes integrate the principles of tribology and materials mechanics, with optimized stripe angles. When material contacts the discharge pipe, the trapezoidal slope generates a normal component force, increasing the effective contact pressure, while the flat-top structure prevents stress concentration and damage to the material surface. The gradient design of the stripe depth creates a gradual distribution of the friction coefficient along the axial direction, effectively suppressing axial movement of the material.

[0063] In this embodiment, the two ends of the rotating support unit 3 are provided with symmetrical limiting retaining rings, which are fixed to the end of the feeding tube by set screws.

[0064] The adjustable limit retaining ring system adopts a split design concept, separating the retaining ring body from the locking function module. The symmetrical arrangement of the two retaining rings forms a dynamic balance constraint system, which can adaptively compensate for the axial dimensional tolerances of the material roll. The elastic gasket on the inner surface of the retaining ring is made of shape memory alloy material, which automatically adjusts the preload force when the temperature changes. The three-dimensional curved contact surface design makes the contact stress distribution between the retaining ring and the material end face more uniform, avoiding the edge stress concentration caused by traditional flat retaining rings.

[0065] Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A linkage feed device characterized by, The device comprises: a machine table; a driving unit comprising a driving motor fixed on the machine table; a rotating support unit comprising a first feeding pipe and a second feeding pipe arranged in parallel and spaced apart, both of which are rotatably arranged on the machine table through a bearing assembly; a linkage adjustment unit having a radially expandable expansion part; a transmission assembly comprising a driving gear connected to the output shaft of the driving motor, a first linkage gear and a second linkage gear both meshing with the driving gear, the first linkage gear meshing with the first feeding pipe and the second feeding pipe and simultaneously driving both of them to rotate, and the second linkage gear meshing with the linkage adjustment unit; The device has two working modes: In the first working mode, the first feeding pipe and the second feeding pipe form a V-shaped support structure, and the torque balance is formed by the weight of the roll-shaped material and the static friction force between the two feeding pipes. When the first feeding pipe and the second feeding pipe rotate, the roll-shaped material synchronously rotates in the opposite direction under the drive of the static friction force to realize feeding. At this time, the expansion part remains in a radially expanded state and forms an elastic constraint on the roll-shaped material; In the second working mode, the linkage adjustment unit is driven to rotate by the second linkage gear, and the expansion part of the linkage adjustment unit is radially expanded and forms an interference fit with the inner wall of the roll-shaped material. The roll-shaped material is fed by the active rotation of the linkage adjustment unit.

2. The linked feed-off apparatus according to claim 1, wherein The first linkage gear and the second linkage gear are located on both opposite sides of the driving gear.

3. The linked feed-off apparatus according to claim 1, wherein The first feeding pipe is provided with a first driven gear, and the second feeding pipe is provided with a second driven gear. The first linkage gear simultaneously meshes with the first driven gear and the second driven gear.

4. The linked feedout apparatus of claim 1, wherein, The expansion part is provided with an array of friction protrusions on the outer periphery.

5. The linked feedout apparatus of claim 1, wherein, In the first working mode, the rotation axis of the expansion part and the rotation axes of the first feeding pipe and the second feeding pipe form a triangular spatial layout.

6. The linked feedout apparatus of claim 1, wherein, The machine table comprises two vertical plates arranged in parallel, and the driving motor is fixedly installed on the back surface of the vertical plates.

7. The linked feedout apparatus of claim 1, wherein, The device further comprises a protective cover covering the outside of the driving gear, the first linkage gear and the second linkage gear.

8. The linked feedout apparatus of claim 1, wherein, The outer surface of the first feeding pipe and the second feeding pipe is provided with axially extending anti-skid stripes, and the cross section of the stripes is trapezoidal protrusions.

9. The linked feedout apparatus of claim 1, wherein, Both ends of the rotating support unit are provided with symmetrical limiting stop rings, and the stop rings are fixed on the end portions of the feeding pipes through tight screws.

10. The linked feedout apparatus of claim 1, wherein, The linkage adjustment unit is provided with a linkage driven gear, and the linkage driven gear meshes with the second linkage gear for transmission.

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