A thick fabric anti-deviation straight knife supporting mechanism

Abstract

The present application belongs to the technical field of cutting bed equipment, and particularly relates to a thick fabric anti-deviation straight knife supporting mechanism. The present application provides a thick fabric anti-deviation straight knife supporting mechanism, which is arranged on a cutting bed head and comprises a central spindle, a cutting knife part, a presser foot assembly, a surface reference part, a swing supporting assembly and a thick material transmission assembly. The presser foot assembly is arranged around the cutting knife part, the surface reference part is synchronously lifted and lowered with the presser foot assembly and transmits the fabric surface height obtained by the presser foot assembly to the supporting mechanism, and the swing supporting assembly is used for providing lateral support for the cutting knife part in the thick material cutting state. The surface reference part is synchronously lifted and lowered with the presser foot assembly, the thickness information of the fabric can be measured and transmitted in real time, the thickness information is converted into the swing action of the swing supporting assembly, the side end of the cutting knife part is automatically resisted in the cutting of the thick fabric, the lateral deviation of the cutting knife part is effectively inhibited, and the size deviation of the upper and lower pieces is obviously reduced.

Description

Technical Field

[0001] This invention belongs to the technical field of cutting equipment, and particularly relates to a straight knife support mechanism for preventing swaying of thick fabrics. Background Technology

[0002] Automatic cutting machines typically complete cutting by moving the machine head laterally. The machine head is equipped with cutting blades that move vertically at high speed under the action of a reciprocating drive mechanism inside the machine head. The cutting blades also change the direction of the blades according to the cutting trajectory, thereby completing the cutting of straight lines, arcs or complex contours.

[0003] Under normal circumstances, the cutting blade experiences less resistance when cutting single-layer or thinner fabrics, but the resistance increases significantly when cutting thicker or multi-layered fabrics. The fiber orientation, interlayer friction, local compaction, and material hardness variations within thick fabrics also cause the forces on both sides of the cutting blade to be uneven. Therefore, the blade is prone to bending and wobbling under high-speed reciprocating conditions, causing the actual cut to deviate from the intended trajectory.

[0004] Existing equipment often incorporates guide wheels or lateral limiting structures around the cutting blade. Some structures utilize fixed-position rollers to constrain the blade, while others use sensors to detect the blade's state and adjust the guiding components. For example, Chinese utility model patent CN205223707U discloses a cutting machine correction mechanism, including a deformable spring sheet. A wheel seat is located within the deformable spring sheet, and a blade is located within the wheel seat. Lateral guide wheels are located on both sides of the blade, and a back guide wheel is located on the back of the blade. A sensor is located at one end of the deformable spring sheet. The sensor is connected to a control system, which is connected to a corner motor. The corner motor has a corner gear pair.

[0005] The patent has proposed the idea of ​​using wheel seats and guide wheels to restrict the area near the cutting blade. However, the existing technology still has the following shortcomings in actual use. In other words, these are the technical problems that this invention aims to solve: 1. The support component is constantly pressed against the surface of the blade, which can easily cause the blade to overheat and affect subsequent cutting; 2. The clearance and contact of the support component do not form a stable feedback with the thickness of the fabric.

[0006] In conclusion, it is necessary to develop an anti-sway straight blade support mechanism that can adjust its position based on fabric thickness feedback to address this problem. Summary of the Invention

[0007] This invention provides a straight blade support mechanism for preventing swaying of thick fabrics. This mechanism is mounted on a cutting machine head and includes a central spindle, a cutting blade, a presser foot assembly, a surface reference component, a swing support assembly, and a thick material transmission assembly. The presser foot assembly surrounds the cutting blade. The surface reference component moves up and down synchronously with the presser foot assembly and transmits the fabric surface height obtained by the presser foot assembly to the support mechanism. The swing support assembly provides lateral support to the cutting blade during thick material cutting. This allows the surface reference component and presser foot assembly to move up and down synchronously, enabling real-time measurement and transmission of fabric thickness information. This thickness information is converted into the swing motion of the swing support assembly, automatically pressing against the side of the cutting blade during thick fabric cutting. This effectively suppresses lateral swaying of the cutting blade and significantly reduces the dimensional deviation between upper and lower layers of cut pieces.

[0008] This invention overcomes the shortcomings of existing technologies and provides a thick fabric anti-sway straight blade support mechanism, installed on a cutting machine head. It includes a central spindle located at the lower end of the cutting machine head, a cutting blade located at the lower end of the central spindle, a presser foot assembly surrounding the cutting blade, a surface reference component that moves synchronously with the presser foot assembly for measuring and transmitting fabric height, a swing support assembly located on the side of the cutting blade to prevent it from swaying, and a thick material transmission assembly that, under the control of a controller, drives the swing support assembly closer to / away from the cutting blade. The surface reference component includes a rotating support carrier sleeved on the outside of the central spindle via a synchronous transmission component, and a follower seat sleeved on the outside of the rotating support carrier via a rotating bearing. The outer periphery of the follower seat is connected to the presser foot assembly and moves up and down with the presser foot assembly along the reciprocating direction of the cutting blade. The thick material transmission assembly includes a vertically mounted component on the side plate of the cutting machine head. A first rack, a transmission support seat mounted on the follower seat, a first transmission shaft rotatably mounted on the transmission support seat, an input gear fixedly mounted on the first transmission shaft and continuously meshing with the first rack, a second transmission shaft horizontally mounted at the end of the first transmission shaft, an output gear mounted on the second transmission shaft, an electromagnetic clutch mounted at the connection between the first and second transmission shafts and selectively connecting the first and second transmission shafts, an annular actuator sleeve axially slidingly sleeved on the outside of the rotating support carrier, a second rack mounted on the annular actuator sleeve and meshing with the output gear, and a radial conversion component mounted at the lower end of the rotating support carrier for converting vertical transmission into horizontal transmission to drive the movement of the swing support assembly; the controller controls the electromagnetic clutch to engage when the thick material condition is met, and controls the electromagnetic clutch to disengage when the thick material condition is not met.

[0009] A further preferred technical solution is that: the radial conversion component includes a rotary control ring axially slidably sleeved on the outside of the rotary support carrier for mounting the annular actuator sleeve, a radial guide groove disposed on the lower end face of the rotary support carrier, a radial actuator slider slidably disposed in the radial guide groove and abutting against the swing support assembly, a convex ring disposed at the lower end of the rotary control ring and extending toward the central main shaft, and an inclined surface disposed on the end face of the convex ring near the radial actuator slider, wherein the convex ring drives the radial actuator slider to slide radially.

[0010] A further preferred technical solution is that the swing support assembly includes a swing arm hinged at its upper end to the rotating support carrier, a blade support head disposed at the lower end of the swing arm, a blade direction roller disposed on the blade support head, and a push roller disposed on the swing arm near the radial actuator slider.

[0011] A further preferred technical solution is that the presser foot assembly includes a presser foot rod vertically arranged around the central spindle, an actuator arranged on the cutting machine head for driving the presser foot rod to rise and fall, and a presser foot ring arranged at the lower end of the presser foot rod.

[0012] A further preferred technical solution is that the synchronous transmission component includes a ball spline shaft fixedly sleeved on the outer periphery of the central spindle, and a ball spline sleeve disposed on the ball spline shaft.

[0013] A further preferred technical solution is that the radial conversion component further includes an axial guide key disposed on the outer surface of the rotary support carrier, and an axial guide groove disposed on the inner circumference of the rotary control ring and connected to the axial guide key.

[0014] A further preferred technical solution is that the swing arm is an integral rigid component.

[0015] A further preferred technical solution is that the swing support assembly further includes a torsion spring disposed at the hinge of the upper end of the swing arm.

[0016] A further preferred technical solution is that: multiple guide posts extend from the lower end of the follower seat, and the annular actuator sleeve is slidably mounted on the guide posts.

[0017] A further preferred technical solution includes a position detection element and a pressure foot force detection element disposed on the pressure foot assembly and electrically connected to the controller.

[0018] The beneficial effects of this invention are at least as follows: 1. The surface reference component and the presser foot assembly synchronously raise and lower, transmitting the fabric thickness information to the thick material transmission component in real time. The controller determines whether the support function is used by engaging and disengaging the electromagnetic clutch. The support function is automatically engaged when cutting thick fabrics and automatically disengaged when cutting relatively thin fabrics. One mechanism simultaneously takes into account multiple working conditions, avoiding overheating under long-term support; 2. No additional drive motor is needed. The power for the support action comes directly from the raising and lowering movement of the presser foot assembly. The structure is simple, the manufacturing cost is low, and the operation is highly reliable; 3. The support component rotates synchronously with the cutting blade, eliminating the need to set up control components to avoid deviations caused by action delays. Attached Figure Description

[0019] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] Figure 1 This is a three-dimensional schematic diagram of the present invention; Figure 2 This is a front view of the present invention; Figure 3 This is a partial three-dimensional schematic diagram of the oblique angle of the present invention; Figure 4 This is a front sectional view of the present invention; Figure 5 This is a partial cross-sectional view of the present invention.

[0021] The meanings of the various reference numerals in the figure are as follows: Cutting machine head (a), fabric (b); 1. Central spindle; 2. Cutting blade assembly; 3. Presser foot assembly; 4. Surface reference assembly; 5. Swing support assembly; 6. Thick material transmission assembly; 31. Presser foot rod, 32. Presser foot ring, 41. Synchronous transmission component, 42. Rotary support carrier, 43. Follower seat, 51. Swing arm, 52. Blade support head, 53. Blade roller, 54. Push roller, 55. Torsion spring, 61. First rack, 62. Transmission support seat, 63. First transmission shaft, 64. Input gear, 65. Second transmission shaft, 66. Output gear, 67. Electromagnetic clutch, 68. Annular actuator sleeve, 69. Second rack, 610. Radial conversion component, 611. Guide post. Ball spline shaft 411, ball spline sleeve 412, rotary control ring 6101, radial guide groove 6102, radial actuator slider 6103, convex ring 6104, inclined surface 6105, axial guide key 6106, axial guide groove 6107. Detailed Implementation

[0022] The embodiments of the present invention will be described in detail below with reference to the accompanying drawings. The following description is only a preferred embodiment of the present invention and is not intended to limit the scope of the present invention.

[0023] The directional terms such as up, down, left, right, front, back, front, back, top, bottom, etc., mentioned or possibly mentioned in this specification are defined relative to the structure shown in the accompanying drawings. The terms "inner" and "outer" refer to the direction toward or away from the geometric center of a specific component, respectively. These are relative concepts and may therefore vary depending on their location and usage. Therefore, these or other directional terms should not be interpreted as restrictive terms.

[0024] As attached Figures 1-5 As shown, a thick fabric anti-sway straight blade support mechanism is installed on a cutting machine head a, including a central spindle 1 located at the lower end of the cutting machine head a, a cutting blade 2 located at the lower end of the central spindle 1, a presser foot assembly 3 surrounding the cutting blade 2, a surface reference 4 that moves synchronously with the presser foot assembly 3 for measuring and transmitting the height of the fabric b, and a swing support assembly 5 located on the side of the cutting blade 2 to prevent the cutting blade 2 from swaying. Under the control of a controller, the swing support assembly 5 is driven to move closer to or further away from the cutting machine head a. The thick material transmission assembly 6 is located away from the cutting blade 2; the surface reference member 4 includes a rotating support carrier 42 sleeved on the outside of the central spindle 1 via a synchronous transmission member 41, and a follower seat 43 sleeved on the outside of the rotating support carrier 42 via a rotating bearing. The outer periphery of the follower seat 43 is connected to the presser foot assembly 3 and moves up and down with the presser foot assembly 3 in the reciprocating direction of the cutting blade 2; the thick material transmission assembly 6 includes a first rack 61 vertically arranged on the side plate of the cutting machine head a, and is arranged on the follower seat 43. The system includes a transmission support 62, a first transmission shaft 63 horizontally rotatably mounted on the transmission support 62, an input gear 64 fixedly mounted on the first transmission shaft 63 and continuously meshing with the first rack 61, a second transmission shaft 65 horizontally mounted at the end of the first transmission shaft 63, an output gear 66 mounted on the second transmission shaft 65, an electromagnetic clutch 67 selectively connecting the first transmission shaft 63 and the second transmission shaft 65 at the connection point, an annular actuator 68 axially slidingly sleeved on the outside of the rotating support carrier 42, a second rack 69 mounted on the annular actuator 68 and meshing with the output gear 66, and a radial conversion member 610 mounted at the lower end of the rotating support carrier 42 for converting vertical transmission into horizontal transmission to drive the movement of the swing support assembly 5. The controller engages the electromagnetic clutch 67 when the thick material condition is met and disengages the electromagnetic clutch 67 when the thick material condition is not met.

[0025] In this embodiment, the thick fabric anti-sway straight blade support mechanism mainly includes the central spindle 1, the cutting blade 2, the presser foot assembly 3, the surface reference component 4, the swing support assembly 5, and the thick material transmission assembly 6. The cutting head a is an existing component on the automatic cutting bed, and it is equipped with a cutting blade driver and a presser foot driver. The central spindle 1 is the C-axis of the cutting bed, preferably a hollow shaft or a combined shaft structure with a central channel, through which the cutting blade 2 passes. The central spindle 1 can also rotate around its own axis to adjust the blade direction of the cutting blade 2.

[0026] The bottom surface of the presser foot assembly 3 presses against the upper surface of fabric b during cutting, serving as the reference surface for measuring the height of fabric b in this invention. The surface reference component 4 includes the synchronous transmission component 41, the rotary support carrier 42, and the follower seat 43. The rotary support carrier 42 is connected to the central spindle 1 via the synchronous transmission component 41, so the rotary support carrier 42 rotates synchronously with the central spindle 1 and can slide up and down along the axial direction of the central spindle 1. The follower seat 43 is sleeved on the outside of the rotary support carrier 42 via a rotary bearing. When the rotary support carrier 42 rotates, the inner ring of the rotary bearing rotates with the rotary support carrier 42, while the outer ring of the rotary bearing and the follower seat 43 do not rotate. The rotary bearing can be a pair of two angular contact ball bearings, with the axial clearance controlled by a preload nut. The outer periphery of the follower seat 43 is fixedly connected to the presser foot assembly 3 and moves up and down along the reciprocating direction of the cutting blade 2. When the follower seat 43 rises and falls, it drives the rotary support carrier 42 to slide up and down along the ball spline shaft 411 via the rotary bearing. Therefore, the working process of the surface reference component 4 is as follows: the presser foot assembly 3 is attached to the surface of the fabric b, providing real-time feedback on the thickness of the fabric b. The height of the follower seat 43 is equal to the thickness of the fabric b plus a fixed difference. The surface reference component 4 transmits the thickness information of the fabric b to the subsequent thick material transmission assembly 6 in a purely mechanical manner.

[0027] The thick material transmission component 6 is the core part that converts the thickness information of fabric b into the swinging motion of the swing support component 5. The first rack 61 is vertically fixed on the side plate of the cutting machine head a, and the rack 61 itself remains stationary. The transmission support 62 is fixedly mounted on the follower seat 43 and extends outwards in parallel, rising and falling with the follower seat 43. The first transmission shaft 63 is horizontally rotatably mounted on the transmission support 62, and the input gear 64 is fixedly mounted on the first transmission shaft 63, continuously meshing with the first rack 61. When the follower seat 43 rises and falls, the input gear 64 rolls along the first rack 61, and the first transmission shaft 63 rotates accordingly. That is, the vertical movement of the follower seat 43 is converted into the rotation of the first transmission shaft 63; the greater the rise and fall, the larger the angle of rotation. The second transmission shaft 65 is coaxially arranged with the first transmission shaft 63, and the electromagnetic clutch 67 is located at the connection between the first transmission shaft 63 and the second transmission shaft 65. When the electromagnetic clutch 67 is engaged, the first drive shaft 63 and the second drive shaft 65 form a transmission connection, and the two shafts rotate together. When the electromagnetic clutch 67 is disengaged, the second drive shaft 65 does not rotate with the first drive shaft 63, and the transmission chain is broken. The output gear 66 is disposed on the second drive shaft 65, and the second rack 69 is vertically disposed on the outer wall of the annular actuator sleeve 68. The output gear 66 meshes with the second rack 69. When the second drive shaft 65 rotates through the electromagnetic clutch 67 connected to the first drive shaft 63, the output gear 66 drives the second rack 69 to move vertically, and the annular actuator sleeve 68 slides axially along the rotating support carrier 42. The radial conversion member 610 is disposed at the lower end of the rotating support carrier 42, and the radial conversion member 610 converts the vertical movement of the annular actuator sleeve 68 into the horizontal swing of the swing support assembly 5. The number of swing support components 5 can be set to one or two sets as needed. When two sets are set, the two sets of swing support components 5 are symmetrically arranged on both sides of the cutter 2. The radial guide groove 6102 and the radial actuator slider 6103 in the radial conversion component 610 are also set to two sets. The two sets of swing support components 5 support the cutter 2 from both sides at the same time. The support forces on both sides of the cutter 2 are balanced with each other, and the anti-sway effect is better.

[0028] The controller engages the electromagnetic clutch 67 when the material thickness condition is met and disengages it when the condition is not met. The material thickness is determined by a pressing test of the presser foot assembly. The fabric's looseness and actual thickness are calculated by the height difference before and after presser foot contact and the presser foot height when the pressure threshold is reached. This avoids unnecessary anti-sway support caused by false thickness differences in soft fabrics resulting from simple height measurements. Furthermore, the controller's control of the electromagnetic clutch 67 includes two processes: delay confirmation and stroke confirmation. Delay confirmation means that after the position and pressure signals exceed the threshold, the controller continuously samples for a period of time. Only when the signals remain above the threshold during the sampling time does the controller engage the electromagnetic clutch 67. This prevents frequent engagement and disengagement of the electromagnetic clutch 67 when the cutting bed passes through areas of localized thickness. Stroke confirmation means that after the electromagnetic clutch 67 engages, the controller checks whether the lifting amount of the follower seat 43 matches the downward movement of the rotation control ring 6101. If they do not match, it indicates a jam in the transmission chain, and the controller immediately alarms and stops the machine. These two processes improve the safety of the mechanism's operation.

[0029] In a preferred embodiment, the radial conversion member 610 includes a rotary control ring 6101 axially slidably sleeved on the outside of the rotary support carrier 42 for mounting the annular actuator sleeve 68, a radial guide groove 6102 disposed on the lower end face of the rotary support carrier 42, a radial actuator slider 6103 slidably disposed in the radial guide groove 6102 and abutting against the swing support assembly 5, a convex ring 6104 disposed at the lower end of the rotary control ring 6101 and extending toward the central main shaft 1, and an inclined surface 6105 disposed on the convex ring 6104 near the end face of the radial actuator slider 6103, wherein the convex ring 6104 drives the radial actuator slider 6103 to slide radially; the radial conversion member 610 also includes an axial guide key 6106 disposed on the outer surface of the rotary support carrier 42, and an axial guide groove 6107 disposed on the inner circumference of the rotary control ring 6101 and connected to the axial guide key 6106.

[0030] In this embodiment, the rotary control ring 6101 is fitted onto the outside of the rotary support carrier 42 via the cooperation of the axial guide key 6106 and the axial guide groove 6107, allowing the rotary control ring 6101 to slide up and down along the rotary support carrier 42. The annular actuator sleeve 68 is mounted on the outer end of the rotary control ring 6101 via a thrust bearing, which allows relative rotation between the two but not relative axial movement. The annular actuator sleeve 68 moves up and down together with the rotary control ring 6101, while the rotary control ring 6101 rotates with the rotary support carrier 42, and the annular actuator sleeve 68 does not rotate. This arrangement has an advantage: the second rack 69 is fixed on the non-rotating annular actuator sleeve 68, and the output gear 66 is also mounted on one side of the non-rotating transmission support 62. The meshing between the output gear 66 and the second rack 69 is not affected by the rotation of the cutting direction, and the meshing relationship remains stable. The rotating convex ring 6104, the radial actuator slider 6103, and the swing support assembly 5 are all mounted on the rotating support carrier 42. They rotate synchronously with the rotating support carrier 42. The convex ring 6104 is a complete annular structure, ensuring alignment with the radial actuator slider 6103 regardless of the rotation angle. The radial guide groove 6102 is located on the lower end face of the rotating support carrier 42 and extends radially. The radial actuator slider 6103 is slidably mounted within the radial guide groove 6102 and can only slide radially. The convex ring 6104 is located at the lower end of the rotating control ring 6101 and extends towards the central main shaft 1. The inclined surface 6105 is located on the end face of the convex ring 6104 near the radial actuator slider 6103, and the inclined surface 6105 has an angle with the vertical direction. When the rotation control ring 6101 moves downward, the convex ring 6104 moves downward accordingly, and the inclined surface 6105 presses against the radial actuator slider 6103. The inclined surface 6105 decomposes the vertical pressure into a radial component, which pushes the radial actuator slider 6103 to slide outward along the radial guide groove 6102. When the rotation control ring 6101 moves upward, the convex ring 6104 moves upward accordingly, the inclined surface 6105 is released, and the radial actuator slider 6103 slides back inward under the action of the restoring force on one side of the swing support assembly 5. In this way, the radial conversion member 610 converts the vertical transmission into horizontal transmission.

[0031] As a preferred embodiment, the swing support assembly 5 includes a swing arm 51 hinged to the upper end of the rotating support carrier 42, a blade support head 52 disposed at the lower end of the swing arm 51, a blade direction roller 53 disposed on the blade support head 52, a push roller 54 disposed on the swing arm 51 near the radial execution slider 6103, and a torsion spring disposed at the upper hinge of the swing arm 51.

[0032] In this embodiment, the swing support assembly 5 includes a swing arm 51, a blade support head 52, a blade-directing roller 53, a pushing roller 54, and a torsion spring. The swing arm 51 is a lever, and its upper end is mounted on the side wall of the rotating support carrier 42 near the central main shaft 1 via a hinge shaft. The swing arm 51 can swing around the hinge shaft. The blade support head 52 is located at the lower end of the swing arm 51, and the blade-directing roller 53 is rotatably mounted on the blade support head 52. The surface of the blade-directing roller 53 makes rolling contact with the side of the cutting blade 2. When the cutting blade 2 moves up and down at high speed, the blade-directing roller 53 rolls on the side of the cutting blade 2. There is rolling friction between them, so the blade-directing roller 53 supports the cutting blade 2 without scratching the blade surface of the cutting blade 2 or significantly increasing the movement resistance of the cutting blade 2. The push roller 54 is rotatably mounted in the middle of the swing arm 51. When the radial actuator slider 6103 moves radially, it pushes the push roller 54, causing the swing arm 51 to swing around the hinge axis. The blade support head 52 swings accordingly and moves closer to the cutting blade 2. The torsion spring 55 is sleeved on the hinge axis at the upper end of the swing arm 51. One end of the torsion spring 55 abuts against the rotating support carrier 42, and the other end abuts against the swing arm 51. The elastic force of the torsion spring 55 keeps the swing arm 51 tending to open away from the cutting blade 2. When the electromagnetic clutch 67 is disengaged, the inclined surface 6105 does not push the radial actuator slider 6103, and the torsion spring 55 pushes the swing arm 51 away, causing the blade roller 53 to move away from the side of the cutting blade 2. The torsion spring 55 ensures that the swing support assembly 5 can reliably reset when the support function is disengaged, and will not rub against the cutting blade 2.

[0033] As a preferred embodiment, the presser foot assembly 3 includes a presser foot rod 31 vertically arranged around the central spindle 1, an actuator arranged on the cutting machine head a for driving the presser foot rod 31 to rise and fall, and a presser foot ring 32 arranged at the lower end of the presser foot rod 31.

[0034] In this embodiment, the actuator is a presser foot driver on the cutting head a. The actuator can be a servo electric cylinder or a cylinder with a proportional valve. The presser foot rod 31 is installed at the lower end of the actuator and is fixedly connected to the follower seat. The presser foot ring 32 is a circular ring with a clearance notch, which surrounds the outside of the cutting blade 2, and there is no contact between the two.

[0035] As a preferred embodiment, the synchronous transmission component 41 includes a ball spline shaft 411 fixedly sleeved on the outer periphery of the central spindle 1, and a ball spline sleeve 412 disposed on the ball spline shaft 411.

[0036] In this embodiment, the rotary support carrier 42 is fixedly connected to the ball spline sleeve 412. The ball spline can transmit torque and allow the shaft and sleeve to slide relative to each other along the axial direction.

[0037] As a preferred embodiment, the swing arm 51 is an integral rigid component.

[0038] In this embodiment, the swing arm 51 is machined from a single piece of aluminum alloy or alloy steel. The integrated rigid structure has two advantages: First, it has good rigidity. The reaction force of the cutting blade 2 on the cutting roller 53 is transmitted to the swing arm 51 through the blade support head 52. The swing arm 51 itself will not undergo significant deformation, and the position of the support point is stable. The second advantage is that there is no joint gap. The swing arm 51 will not loosen or wobble during vibration, and the support accuracy is high.

[0039] As a preferred embodiment, the lower end of the follower seat 43 extends out with a plurality of guide posts 611, and the annular actuator sleeve 68 is slidably mounted on the guide posts 611.

[0040] In this embodiment, the annular actuator sleeve 68 is provided with a sliding hole corresponding to the guide post 611, and the guide post 611 passes through the sliding hole. The guide post 611 guides the up-and-down movement of the annular actuator sleeve 68, making the movement of the annular actuator sleeve 68 more stable. At the same time, the guide post 611 is fixed on the follower seat 43, and the follower seat 43 does not rotate, so the guide post 611 also restricts the rotation of the annular actuator sleeve 68, ensuring that the second rack 69 on the annular actuator sleeve 68 is always aligned with the output gear 66.

[0041] As a preferred embodiment, it further includes a position detection element and a pressure foot force detection element disposed on the pressure foot assembly 3 and electrically connected to the controller.

[0042] In this embodiment, the position detection element is disposed on the presser foot rod 31. The position detection element can be a wire encoder to detect the position of the presser foot rod 31 in real time, and the controller calculates the thickness of the fabric b based on this position. The presser foot force detection element is disposed between the presser foot rod 31 and the presser foot ring 32. A strain gauge pressure sensor can be used to detect the pressure of the presser foot ring 32 pressing on the fabric b in real time. Both the position detection element and the presser foot force detection element are electrically connected to the controller. The controller combines the position signal and the pressure signal to determine whether the material thickness condition is met, and the judgment result is more reliable. For example, when uneven fabric laying causes local bulges, the position signal will be larger, but the pressure signal will not increase synchronously. The controller can identify this situation and prevent the electromagnetic clutch 67 from engaging incorrectly. As another example, when the presser foot ring 32 presses against a foreign object on the table, the pressure signal will suddenly increase, but the position signal will not change synchronously. The controller can also identify this situation.

[0043] The overall working principle of the thick fabric anti-sway straight knife support mechanism is explained below in conjunction with two motion phases: During the non-thick fabric cutting stage, fabric b has a smaller thickness, the presser foot assembly 3 is positioned lower, the height measured by the position detection element is lower than the set height threshold, and the pressure measured by the presser foot force detection element is lower than the set pressure threshold. The controller determines that the thick material condition is not met, and the electromagnetic clutch 67 remains disengaged. At this time, the follower seat 43 rises and falls with the presser foot assembly 3, the input gear 64 rolls along the first rack 61, the first drive shaft 63 idles, and the electromagnetic clutch 67 disconnects the transmission connection between the first drive shaft 63 and the second drive shaft 65, so the second drive shaft 65 does not rotate. The annular actuator sleeve 68 and the rotation control ring 6101 remain in their initial high positions. The torsion spring 55 pushes the swing arm 51 open, and a gap is left between the cutter roller 53 and the side of the cutting blade 2. The cutting process of the cutting blade 2 is undisturbed, and its working state is exactly the same as that of a normal cutting bed.

[0044] During the thick fabric cutting stage, the fabric b is thicker, the presser foot assembly 3 is positioned higher, the height measured by the position detection element exceeds the set height threshold, the pressure measured by the presser foot force detection element exceeds the set pressure threshold, the controller determines that the thick material condition is met, and the electromagnetic clutch 67 engages. At this time, the height of the follower seat 43 corresponds to the actual thickness of the fabric b, the input gear 64 rolls along the first rack 61, the rotation angle of the first transmission shaft 63 corresponds to the lifting and lowering amount of the follower seat 43, after the electromagnetic clutch 67 is engaged, the first transmission shaft 63 drives the second transmission shaft 65 to rotate, the output gear 66 drives the second rack 69 to move vertically, the annular actuator sleeve 68 and the rotation control ring 6101 move down along the rotation support carrier 42, the convex ring 6104 moves down with the rotation control ring 6101, the inclined surface 6105 pushes the radial actuator slider 6103, the radial actuator slider 6103 slides outward along the radial guide groove 6102, the radial actuator slider 6103 pushes the pushing roller 54, the swing arm 51 swings around the hinge axis against the elastic force of the torsion spring 55, and the blade roller 53 abuts against the side of the cutting blade 2. When the cutting blade 2 is cutting thick fabric, it is subjected to lateral force. The cutting roller 53 supports the cutting blade 2 from the side, and the sway of the cutting blade 2 is suppressed.

[0045] The entire working process has a natural linkage: the thicker the fabric b, the higher the presser foot assembly 3, the greater the lifting and lowering of the follower seat 43, the greater the downward movement of the rotation control ring 6101, the larger the swing angle of the swing arm 51, and the lower and closer the blade support head 52 is to the working section of the cutting blade 2. The thicker the fabric, the longer the working section of the blade, and the lower the support point is aligned perfectly with the working section. When the thickness decreases, the working section of the blade is shorter, and the support point moves upward to avoid the blade tip. Therefore, the position of the support point always automatically adjusts according to the thickness of the fabric b, without requiring manual adjustment.

[0046] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit it. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all such modifications or substitutions should be covered within the scope of the present invention.

Claims

1. A straight blade support mechanism for preventing swaying of thick fabric, mounted on the head of a cutting machine, characterized in that, It includes a central spindle located at the lower end of the cutting machine head, a cutting blade located at the lower end of the central spindle, a presser foot assembly surrounding the cutting blade, a surface reference component that moves synchronously with the presser foot assembly for measuring and transmitting fabric height, a swing support assembly located at the side of the cutting blade for preventing the cutting blade from swaying, and a thick material transmission assembly that drives the swing support assembly to move closer to / away from the cutting blade under the control of the controller. The surface reference component includes a rotating support carrier sleeved on the outside of the central main shaft via a synchronous transmission component, and a follower seat sleeved on the outside of the rotating support carrier via a rotating bearing. The outer periphery of the follower seat is connected to the presser foot assembly and moves up and down along the reciprocating direction of the cutter component with the presser foot assembly. The thick material transmission assembly includes a first rack vertically mounted on the side plate of the cutting machine head, a transmission support seat mounted on the follower seat, a first transmission shaft horizontally rotatably mounted on the transmission support seat, an input gear fixedly mounted on the first transmission shaft and continuously meshing with the first rack, a second transmission shaft horizontally mounted at the end of the first transmission shaft, an output gear mounted on the second transmission shaft, an electromagnetic clutch mounted at the connection between the first and second transmission shafts and selectively connecting the first and second transmission shafts, an annular actuator sleeve axially slidably mounted on the outside of the rotating support carrier, a second rack mounted on the annular actuator sleeve and meshing with the output gear, and a radial conversion member mounted at the lower end of the rotating support carrier for converting vertical transmission into horizontal transmission to drive the movement of the swing support assembly; The controller engages the electromagnetic clutch when the material thickness condition is met, and disengages the electromagnetic clutch when the material thickness condition is not met.

2. The anti-sway straight knife support mechanism for thick fabric according to claim 1, characterized in that, The radial conversion component includes a rotary control ring axially slidably sleeved on the outside of the rotary support carrier for mounting the annular actuator sleeve, a radial guide groove disposed on the lower end face of the rotary support carrier, a radial actuator slider slidably disposed in the radial guide groove and abutting against the swing support assembly, a convex ring disposed at the lower end of the rotary control ring and extending toward the central main shaft, and an inclined surface disposed on the end face of the convex ring near the radial actuator slider, wherein the convex ring drives the radial actuator slider to slide radially.

3. The anti-sway straight knife support mechanism for thick fabric according to claim 2, characterized in that, The swing support assembly includes a swing arm hinged at its upper end to the rotary support carrier, a blade support head disposed at the lower end of the swing arm, a blade direction roller disposed on the blade support head, and a push roller disposed on the swing arm near the radial actuator slider.

4. The anti-sway straight knife support mechanism for thick fabric according to claim 1, characterized in that, The presser foot assembly includes a presser foot bar vertically arranged around the central spindle, an actuator arranged on the cutting machine head for driving the presser foot bar to rise and fall, and a presser foot ring arranged at the lower end of the presser foot bar.

5. The anti-sway straight knife support mechanism for thick fabric according to claim 1, characterized in that, The synchronous transmission component includes a ball spline shaft fixedly sleeved on the outer periphery of the central spindle, and a ball spline sleeve disposed on the ball spline shaft.

6. The anti-sway straight knife support mechanism for thick fabric according to claim 2, characterized in that, The radial conversion component also includes an axial guide key disposed on the outer surface of the rotary support carrier, and an axial guide groove disposed on the inner circumference of the rotary control ring and connected to the axial guide key.

7. The anti-sway straight knife support mechanism for thick fabric according to claim 3, characterized in that, The swing arm is a one-piece rigid component.

8. The anti-sway straight knife support mechanism for thick fabric according to claim 1, characterized in that, The swing support assembly also includes a torsion spring disposed at the upper hinge of the swing arm.

9. The anti-sway straight knife support mechanism for thick fabric according to claim 1, characterized in that, Multiple guide posts extend from the lower end of the follower seat, and the annular actuator sleeve is slidably mounted on the guide posts.

10. A thick fabric anti-sway straight knife support mechanism according to claim 1, characterized in that, It also includes a position detection element and a pressure foot force detection element disposed on the pressure foot assembly and electrically connected to the controller.

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