Transmission device and laver processing equipment

Abstract

The invention provides a transmission device and laver processing equipment, and relates to the technical field of transmission devices.The transmission device comprises a driving disc, an intermittent disc and a connecting assembly, the driving disc is provided with a first cam part and a second cam part, and the first cam part and the second cam part are arranged at intervals in the radial direction of a first mandrel and form channels with the same width; the first arc section is provided with a first curved surface formed on the first cam part, and the second arc section is provided with a second curved surface formed on the second cam part; the intermittent disc is provided with a sliding block and has a first motion state and a second motion state, in the first motion state, the sliding block is in sliding fit with the first curved surface, and in the second motion state, the sliding block is in sliding fit with the second curved surface; the connecting assembly comprises a tooth-shaped part and a tooth groove part, one of the tooth-shaped part and the tooth groove part is arranged on the second cam part, the other of the tooth-shaped part and the tooth groove part is arranged on the intermittent disc, and when the sliding block is located on the turning section, the tooth-shaped part and the tooth groove part are in meshed transmission. The device can run stably, and is simple in overall structure and high in working reliability.

Description

Technical Field

[0001] The present invention relates to the technical field of transmission devices, and particularly to a transmission device and laver processing equipment. Background Art

[0002] The head claw chain in the laver processing unit performs intermittent motion, and the large box feather chain performs continuous motion. To accurately complete the handover of the curtain frame component between the head and the large box, an intermittent transmission device is required to ensure the motion coordination between the head claw chain and the large box feather chain.

[0003] However, in the intermittent transmission devices in the related art, the intermittent motion law is often parabolic with zero starting speed increase - maximum speed - zero speed stop. When the laver processing unit moves at a relatively high machine speed (i.e., a relatively fast intermittent frequency), near the maximum speed point, the running speed of the curtain frame is too fast, and the prefabricated laver cakes on the curtain frame are prone to dispersion due to shaking, resulting in a decrease in the overall running stability and working reliability of the laver processing unit, thereby restricting the speed increase and efficiency improvement of the laver processing unit. Summary of the Invention

[0004] The present invention aims to solve at least one of the technical problems in the related art to some extent.

[0005] To this end, an embodiment of one aspect of the present invention provides a transmission device, which can operate smoothly, has a simple overall structure, and strong working reliability.

[0006] An embodiment of another aspect of the present invention provides a laver processing equipment.

[0007] A transmission device according to an embodiment of the present invention includes a driving disk, an intermittent disk, and a handover component. The driving disk is pivotable about the axis of a first core shaft. The driving disk is provided with a first cam portion and a second cam portion. The first cam portion and the second cam portion are arranged at intervals in the radial direction of the first core shaft and define an equal-width channel. The channel includes a first arc segment, a direction-changing segment, and a second arc segment connected in sequence. The first arc segment has a first curved surface formed on the first cam portion, and the second arc segment has a second curved surface formed on the second cam portion. The intermittent disk is pivotable about the axis of a second core shaft. The axial direction of the second core shaft is the same as the axial direction of the first core shaft. The intermittent disk is provided with a slider and has a first motion state and a second motion state. In the first motion state, the slider is in sliding cooperation with the first curved surface. In the second motion state, the slider is in sliding cooperation with the second curved surface. The handover component includes a tooth-shaped portion and a tooth groove portion. One of the tooth-shaped portion and the tooth groove portion is provided on the second cam portion, and the other is provided on the intermittent disk. When the slider is located in the direction-changing segment, the tooth-shaped portion and the tooth groove portion are engaged for transmission.

[0008] According to the transmission device of the embodiment of the present invention, the first core shaft can drive the driving disk to rotate so that the slider on the intermittent disk can slide along the groove. During this process, after the slider enters the groove, it is first subjected to the force of the first curved surface, and the intermittent disk is in a first motion state and rotates around the second core shaft. Afterwards, the slider slides to the direction-changing section, and the force direction of the slider will change in the direction-changing section, that is, the force acting on the slider is switched from the first curved surface to the second curved surface, so that the intermittent disk is in a second motion state and rotates when the slider is subjected to the force of the second curved surface, wherein the groove can produce a restraining and limiting effect on the slider, so that the rotation of the intermittent disk is completely controlled by the driving disk, thereby avoiding the intermittent disk self-rotation that may occur due to unexpected shutdown. The problem of misalignment, interference or mutual damage of mechanical parts occurs. However, in the turning section, the restraining and limiting ability of the groove on the slider will be weakened. At this time, if the intermittent disk is shaken by external force, the intermittent disk will shake significantly, thereby reducing the motion accuracy of the transmission device. The handover assembly can increase the transmission accuracy and reduce the severe impact of the slider caused by the sudden change in the force direction when the slider passes through the turning section through the meshing transmission between the tooth-shaped part and the tooth groove part, effectively preventing the risk of damage to the slider under large load conditions, improving the stability of the transmission, and ensuring the continuous, reliable and stable driving of the intermittent disk by the drive disk. Therefore, compared with the related technology, the present invention can run smoothly, the overall structure is simple, and the working reliability is strong.

[0009] In some embodiments, the first arc segment and the second arc segment are mirror-symmetric relative to a reference plane, the axis of the first core shaft coincides with the reference plane, and on a projection plane perpendicular to the axial direction of the first core shaft, the curvature of the projection of the first arc segment gradually increases in a direction from the first arc segment toward the turning segment.

[0010] In some embodiments, the direction-changing section is arranged on the driving disk with the reference plane as the symmetric center, the direction-changing section is concave toward the first core shaft, and when the slider is slidably matched with the direction-changing section, the intermittent disk moves at a constant speed relative to the driving disk;

[0011] Any one of the tooth-shaped portion and the tooth groove portion is arranged on the second cam portion with the reference plane as the symmetry center and is adjacent to a position of the direction-changing section that is closest to the first core shaft.

[0012] In some embodiments, the slider is pivotally connected to the intermittent disk, and an outer contour of a cross section of the slider is circular.

[0013] In some embodiments, the number of the sliders is N, N ≥ 2n, wherein n is an integer greater than or equal to 2, and all the sliders are arranged at equal intervals along the circumference of the intermittent disk;

[0014] The tooth-shaped portion is arranged on the outer peripheral surface of the intermittent disk and extends along the radial direction of the second core shaft. The slider is located between the tooth-shaped portion and the second core shaft along the radial direction of the second core shaft. There are multiple tooth-shaped portions and they correspond to the sliders one by one.

[0015] In some embodiments, the driving disk is further provided with a ring body, and the ring body and the first cam portion are both located on the outer peripheral side of the second cam portion and are arranged at intervals along the circumference of the first core shaft;

[0016] At least one of the ring body and the second cam portion has an arc surface, and the arc surface is cocentric with the first core shaft. The intermittent disk also has a static state, and the slider is slidably matched with the arc surface in the static state.

[0017] A laver processing device according to an embodiment of the present invention comprises a machine head claw chain assembly, a curtain frame, a large box feather chain assembly, a transmission device and a frame, wherein the machine head claw chain assembly is used to convey the curtain frame, the curtain frame can carry laver materials, and the large box feather chain assembly is connected with the machine head claw chain assembly to transport the curtain frame; the transmission device is the transmission device described in any of the above embodiments, the first mandrel of the transmission device is transmission-connected to the large box feather chain assembly, and the second mandrel of the transmission device is transmission-connected to the machine head claw chain assembly; the machine head claw chain assembly, the large box feather chain assembly and the transmission device are all installed on the frame.

[0018] In the laver processing equipment according to the embodiment of the present invention, the transmission device is designed as a structure in which a groove, a slider and a connecting component cooperate with each other, which not only allows the rotation of the intermittent disk to be completely controlled by the driving disk to ensure the working reliability of the transmission device, but also enables the driving disk to continuously and stably drive the intermittent disk to perform intermittent motion. Therefore, compared with the related art, the laver processing equipment using the transmission device has improved operating smoothness and reliability, low operating noise, and can achieve the purpose of speeding up and increasing efficiency.

[0019] In some embodiments, the head claw chain assembly includes a first sprocket and a second sprocket, the first sprocket is pivotally connected to the frame, and the second sprocket is sleeved on the second spindle and is transmission-connected to the first sprocket through a claw chain.

[0020] In some embodiments, the head claw chain assembly also includes a chain claw, which is installed on the claw chain and is suitable for clamping the curtain frame. There are multiple chain claws and they are arranged at intervals along the conveying direction of the claw chain. The distance between any two adjacent chain claws is greater than the length of the curtain frame.

[0021] In some embodiments, the laver processing device further includes a third sprocket and a fourth sprocket. The third sprocket is sleeved on the first mandrel. The fourth sprocket is pivotally mounted on the frame and is in transmission connection with the third sprocket through a transition chain. The fourth sprocket is in transmission connection with the large box feather chain assembly.

[0022] In some embodiments, the large box feather chain assembly includes a fifth sprocket, a sixth sprocket, and feather chain rods. The fifth sprocket is coaxially connected to the fourth sprocket. The sixth sprocket is pivotally mounted on the frame and is in transmission connection with the fifth sprocket through a feather chain. The feather chain rods are mounted on the feather chain and protrude from the feather chain. There are a plurality of feather chain rods, which are arranged at intervals along the conveying direction of the feather chain. Any two adjacent feather chain rods and the feather chain jointly define a receiving groove for receiving the curtain rack.

[0023] Additional aspects and advantages of the present invention will be given in part in the following description, become apparent in part from the following description, or be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 is a schematic structural diagram of a transmission device according to an embodiment of the present invention.

[0025] Figure 2 is a first schematic structural diagram of a driving disk in the transmission device according to an embodiment of the present invention.

[0026] Figure 3 is a second schematic structural diagram of a driving disk in the transmission device according to an embodiment of the present invention.

[0027] Figure 4 is a third schematic structural diagram of a driving disk in the transmission device according to an embodiment of the present invention.

[0028] Figure 5 is a schematic structural diagram of an intermittent disk in the transmission device according to an embodiment of the present invention.

[0029] Figure 6 is a schematic structural diagram of the intermittent disk in the transmission device according to an embodiment of the present invention in a first motion state, and the slider is at the entrance of the channel.

[0030] Figure 7 is a schematic structural diagram of the intermittent disk in the transmission device according to an embodiment of the present invention in a first motion state, and the slider is engaged with the first arc segment.

[0031] Figure 8 is a schematic structural diagram of the intermittent disk in the transmission device according to an embodiment of the present invention switching from the first motion state to the second motion state, and the slider is engaged with the direction-changing segment Figure One .

[0032] Figure 9 Schematic diagram of the intermittent disk in the transmission device according to an embodiment of the present invention switching from the first motion state to the second motion state, and the slider cooperating with the deflection section Figure Two .

[0033] Figure 10 Schematic diagram of the intermittent disk in the transmission device according to an embodiment of the present invention switching from the first motion state to the second motion state, and the slider cooperating with the deflection section Figure Three .

[0034] Figure 11 Schematic diagram of the intermittent disk in the transmission device according to an embodiment of the present invention switching from the first motion state to the second motion state, and the slider cooperating with the deflection section Figure Four .

[0035] Figure 12 Schematic diagram of the transmission device according to an embodiment of the present invention, where the intermittent disk is in the second motion state and the slider is at the outlet of the channel

[0036] Figure 13 Schematic diagram of the transmission device according to an embodiment of the present invention when the intermittent disk is in the stationary state

[0037] Figure 14 Schematic diagram of the laver processing equipment according to an embodiment of the present invention

[0038] Reference numerals:

[0039] 10, laver processing equipment;

[0040] 100, transmission device;

[0041] 1, drive disk; 11, first cam portion; 12, second cam portion; 13, channel; 131, first arc segment; 1311, first curved surface; 132, deflection section; 133, second arc segment; 1331, second curved surface; 14, ring body; 15, circular arc surface;

[0042] 2, intermittent disk; 21, slider;

[0043] 3, transfer assembly; 31, tooth-shaped portion; 32, tooth groove portion;

[0044] 4, first core shaft;

[0045] 5, second core shaft;

[0046] 6, head claw chain assembly; 61, first sprocket; 62, second sprocket; 63, claw chain; 64, chain claw;

[0047] 7, curtain rack;

[0048] 8. Large box feather chain assembly; 81. Fifth sprocket; 82. Sixth sprocket; 83. Feather chain rod; 84. Feather chain; 85. Accommodating groove;

[0049] 91. Third sprocket; 92. Fourth sprocket; 93. Transition chain. Detailed implementation manner

[0050] The embodiments of the present invention will be described in detail below. The examples of the embodiments are shown in the accompanying drawings. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to explain the present invention and should not be construed as limiting the present invention.

[0051] As Figures 1 to 5 shown, a transmission device 100 according to an embodiment of the present invention includes a driving disk 1, an intermittent disk 2, and a handover assembly 3. The driving disk 1 is pivotable about the axis of a first core shaft 4. The driving disk 1 is provided with a first cam portion 11 and a second cam portion 12. The first cam portion 11 and the second cam portion 12 are arranged at intervals in the radial direction of the first core shaft 4 and define a channel 13 of equal width. The channel 13 includes a first arc segment 131, a direction-changing segment 132, and a second arc segment 133 that are connected in sequence. The first arc segment 131 has a first curved surface 1311 formed on the first cam portion 11, and the second arc segment 133 has a second curved surface 1331 formed on the second cam portion 12. The intermittent disk 2 is pivotable about the axis of a second core shaft 5. The axial direction of the second core shaft 5 is the same as the axial direction of the first core shaft 4. The intermittent disk 2 is provided with a slider 21 and has a first motion state and a second motion state. In the first motion state, the slider 21 is in sliding cooperation with the first curved surface 1311. In the second motion state, the slider 21 is in sliding cooperation with the second curved surface 1331. In other words, when the intermittent disk 2 is in the first motion state, the slider 21 is rotated by the action of the first curved surface 1311, and when the intermittent disk 2 is in the second motion state, the slider 21 is rotated by the action of the second curved surface 1331. The handover assembly 3 includes a tooth-shaped portion 31 and a tooth groove portion 32. One of the tooth-shaped portion 31 and the tooth groove portion 32 is provided on the second cam portion 12, and the other is provided on the intermittent disk 2. When the slider 21 is located at the direction-changing segment 132, the tooth-shaped portion 31 and the tooth groove portion 32 are in meshing transmission to cause the intermittent disk 2 to switch from the first motion state to the second motion state.

[0052] According to the transmission device 100 of the embodiment of the present invention, the first core shaft 4 can drive the driving disk 1 to rotate, so that the slider 21 on the intermittent disk 2 can slide along the groove 13. During this process, after the slider 21 enters the groove 13, it is first subjected to the force of the first curved surface 1311, and the intermittent disk 2 is in a first motion state and rotates around the second core shaft 5. After that, the slider 21 slides to the direction-changing section 132, and the force direction of the slider 21 will change in the direction-changing section 132, that is, the force acting on the slider 21 is switched from the first curved surface 1311 to the second curved surface 1331, so that the intermittent disk 2 is in the second motion state and rotates when the slider 21 is subjected to the force of the second curved surface 1331, wherein the groove 13 can produce a restraining and limiting effect on the slider 21, so that the rotation of the intermittent disk 2 is completely controlled by the driving disk 1 to avoid accidental stop. The intermittent disk 2 may rotate on its own, causing misalignment, interference or mutual damage to the machine parts. However, in the turning section 132, the restraining and limiting ability of the groove 13 on the slider 21 will be weakened. At this time, if the intermittent disk 2 is shaken by external force, the intermittent disk 2 will shake significantly, thereby reducing the movement accuracy of the transmission device 100. The intersection component 3 can increase the transmission accuracy through the meshing transmission between the tooth-shaped portion 31 and the tooth groove portion 32 when the slider 21 passes through the turning section 132, and reduce the severe impact of the sudden change in the force direction on the slider 21, effectively preventing the risk of damage to the slider 21 under high load conditions, improving the stability of the transmission, and ensuring the continuous, reliable and stable driving of the drive disk 1 to the intermittent disk 2. Therefore, compared with the related art, the present invention can run smoothly, has a simple overall structure and strong working reliability.

[0053] It can be understood that “the driving disc 1 can pivot around the axis of the first spindle 4”, that is, the driving disc 1 is sleeved on the first spindle 4, and when the first spindle 4 is driven to rotate by a driver or manually, the driving disc 1 will rotate synchronously therewith. Similarly, “the intermittent disc 2 can pivot around the axis of the second spindle 5”, that is, the intermittent disc 2 is sleeved on the second spindle 5, and when the intermittent disc 2 is driven to rotate by the driving disc 1, the second spindle 5 can rotate synchronously therewith.

[0054] In addition, in some embodiments of the present invention, the tooth-shaped portion 31 is provided on the second cam portion 12, and the tooth groove portion 32 is provided on the intermittent disk 2; in other embodiments, the tooth groove portion 32 is provided on the second cam portion 12, and the tooth-shaped portion 31 is provided on the intermittent disk 2. Therefore, the layout of the intersection component 3 of the present invention can be the above-mentioned two methods respectively.

[0055] Specifically, the driving disk 1 can be coaxially connected to the first mandrel 4, that is, the center of the driving disk 1 can be provided with a first through hole extending in the thickness direction thereof, and the first mandrel 4 can be coaxially fixedly installed in the first through hole, so that the driving disk 1 can be driven by a driver or manually to rotate. The width of the groove 13 is equal to or slightly larger than the size specification of the slider 21, so that the slider 21 can be slidably constrained by the groove 13. The groove 13 can have two openings, namely an inlet and an outlet, wherein the inlet is located at the end of the first arc segment 131 away from the redirecting segment 132, and the outlet is located at the end of the second arc segment 133 away from the redirecting segment 132. When the driving disk 1 rotates, the slider 21 can enter the groove 13 from the inlet and escape from the constraint and drive of the groove 13 from the outlet. The first arc segment 131, the redirecting segment 132 and the second arc segment 133 are arranged in sequence along the extension direction of the groove 13. The intermittent disk 2 can be coaxially connected to the second mandrel 5, that is, the center of the intermittent disk 2 can be provided with a second through hole extending in the thickness direction thereof, and the second mandrel 5 can be coaxially fixedly installed in the second through hole. The first mandrel 4 and the second mandrel 5 are arranged at intervals along the radial direction of the first mandrel 4. The tooth groove portion 32 can be a mounting block with tooth grooves, such as the tooth groove portion 32 can be fixed to the second cam portion 12 by bolts, or the tooth groove portion 32 can be integrally formed on the second cam portion 12.

[0056] like Figures 1 to 4 As shown, in some embodiments, the first arc segment 131 and the second arc segment 133 are mirror-symmetrical relative to a reference plane, the axis of the first core shaft 4 coincides with the reference plane, and on the axial projection plane perpendicular to the first core shaft 4, the curvature of the projection of the first arc segment 131 gradually increases in the direction from the first arc segment 131 toward the turning segment 132.

[0057] It can be understood that since the first arc segment 131 and the second arc segment 133 are arranged in mirror symmetry, when the curvature of the projection of the first arc segment 131 gradually increases in the direction from the first arc segment 131 toward the turning segment 132, the curvature of the projection of the second arc segment 133 gradually decreases in the direction from the turning segment 132 toward the second arc segment 133, so that when the driving disk 1 rotates and the slider 21 slides along the groove 13, the sliding speed of the slider 21 can start from zero speed and gradually increase in the first arc segment 131, and gradually decrease to zero speed in the second arc segment 133.

[0058] At the same time, designing the first arc segment 131 and the second arc segment 133 as a mirror-symmetrical structure is also conducive to the processing and forming of the groove 13, reducing the production difficulty of the transmission device 100 and simplifying its overall structure.

[0059] like Figures 1 to 4As shown, in some embodiments, the deflection section 132 is disposed on the drive disk 1 with the reference plane as the center of symmetry, and the deflection section 132 is concave toward the first mandrel 4. In other words, on the projection plane perpendicular to the axial direction of the first mandrel 4, the projection of the deflection section 132 is a concave pit structure that is mirror-symmetrical. When the slider is slidably engaged with the deflection section, the intermittent disk moves at a constant speed relative to the drive disk. At this time, on the projection plane perpendicular to the axial direction of the first mandrel 4, the curvature of the projection of the deflection section 132 first gradually increases and then gradually decreases. That is, the curvature of the projection of the deflection section 132 gradually increases along the direction from the first arc section 131 toward the position closest to the first mandrel 4, and gradually decreases along the direction from the position closest to the first mandrel 4 toward the second arc section 133, so as to minimize the influence of the sudden change in the shape of the deflection section 132 on the smooth sliding of the slider 21, and the minimum curvature of the projection of the deflection section 132 is equal to the maximum curvature of the projection of the first arc section 131.

[0060] It can be understood that, in combination with the structural design of the above-mentioned first arc section 131 and second arc section 133, and the curvature of the projection of the deflection section 132 is designed to first gradually increase and then gradually decrease, so that when the drive disk 1 rotates, the intermittent disk 2 can start accelerating from zero (i.e., the first arc section 131 is the acceleration section) - operate at a constant speed (i.e., the deflection section 132 is the constant speed section) - decelerate and stop (i.e., the second arc section 133 is the deceleration section). At this time, the slider 21 can move at a constant speed at the highest speed in the deflection section 132.

[0061] It should be noted that the curvature parameters of the projections of each of the first arc section 131, the deflection section 132, and the second arc section 133 of the channel 13 can be designed and adjusted accordingly according to actual needs. Therefore, compared with the transmission mechanism of the radial multi-groove intermittent wheel in the related art, the present invention has a variable design of the operating curve and operates more smoothly.

[0062] In addition, by adjusting the extension length of each of the first arc section 131, the deflection section 132, and the second arc section 133, the movement duration of the intermittent disk 2 in the acceleration section, the constant speed section, and the deceleration section can be changed, which is beneficial to improving the speed and efficiency of the laver processing unit when the transmission device 100 is applied to the laver processing unit.

[0063] Either the tooth profile part 31 or the tooth groove part 32 is disposed on the second cam part 12 with the reference plane as the center of symmetry and adjacent to the position of the deflection section 132 closest to the first mandrel 4. That is to say, the tooth profile part 31 or the tooth groove part 32 is also a mirror-symmetrical structure and corresponds exactly to the concave pit of the deflection section 132, that is, the tooth profile part 31 or the tooth groove part 32 is disposed at the middle position adjacent to the deflection section 132.

[0064] It can be understood that with the above structural design of the deflection section 132, the structure of the channel 13 can be further simplified, which is beneficial to the machining and forming of the channel 13.

[0065] It should be noted that the interface component 3 mainly plays a transition and connection role near the middle position of the redirecting section 132 to prevent the sudden change of shape at this position from causing serious impact problems on the slider 21, and the scope of action of the redirecting section 132 on the slider 21 is greater than the scope of action of the interface component 3 on the slider 21. In addition, in order to prevent over-positioning or interference in driving, the gap at the position corresponding to the scope of action of the interface component 3 on the redirecting section 132 can be slightly enlarged, that is, the width of the groove 13 at this position is slightly larger, so that only the interface component 3 plays a driving role on the slider 21 at this position.

[0066] like Figure 1 and Figure 5 As shown, in some embodiments, the slider 21 is pivotally connected to the intermittent disk 2 , and the outer contour of the cross section of the slider 21 is circular to ensure that the slider 21 runs smoothly in the groove 13 and reduce the wear on the slider 21 .

[0067] For example, the slider 21 may not be limited to a columnar slider 21 , such as a bearing, so that the outer circumference of the slider 21 is in rolling contact with the groove 13 , and at this time, the width of the groove 13 is equal to or slightly larger than the outer diameter of the slider 21 .

[0068] like Figure 5 As shown, in some embodiments, the number of sliders 21 is N, N ≥ 2n, where n is an integer greater than or equal to 2, that is, the number of sliders 21 is an even number. For example, the number of sliders 21 can be 4, 6, 8, etc., but is not limited to the listed values, and other values ​​not listed in the numerical range are also applicable. All sliders 21 are arranged at equal intervals along the circumference of the intermittent disk 2.

[0069] The toothed portion 31 is provided on the outer circumference of the intermittent disk 2 and extends in the radial direction of the second mandrel 5. The slider 21 is located between the toothed portion 31 and the second mandrel 5 in the radial direction of the second mandrel 5. In other words, on the projection plane perpendicular to the axial direction of the second mandrel 5, the projection of the toothed portion 31 and the projection of the slider 21 are located on the same radial line of the second mandrel 5, and the slider 21 is closer to the second mandrel 5 than the toothed portion 31. For example, the toothed portion 31 is formed on the outer circumference of the intermittent disk 2, and the slider 21 is rotatably mounted on the end face of the intermittent disk 2. There are multiple toothed portions 31 and they correspond to the sliders 21 one by one, that is, the number of toothed portions 31 is equal to the number of sliders 21.

[0070] like Figure 3 and Figure 4 As shown, in some embodiments, the drive disk 1 is further provided with a ring body 14, and the ring body 14 and the first cam portion 11 are both located on the outer peripheral side of the second cam portion 12 and are arranged at intervals along the circumference of the first core shaft 4. At this time, a groove 13 is jointly constructed between the inner peripheral surface of the first cam portion 11 and the outer peripheral surface of the second cam portion 12.

[0071] At least one of the annular body 14 and the second cam portion 12 has an arc surface 15. That is to say, in some embodiments of the present invention, the annular body 14 has an arc surface 15; in other embodiments, the second cam portion 12 has an arc surface 15; in still other embodiments, both the annular body 14 and the second cam portion 12 have an arc surface 15. Therefore, the arrangement of the arc surface 15 of the present invention can be any of the aforementioned three ways. The arc surface 15 is concentric with the first mandrel 4, and the intermittent disk 2 also has a stationary state. The slider 21 is in sliding fit with the arc surface 15 in the stationary state. In other words, when the slider 21 is in sliding fit with the arc surface 15, the intermittent disk 2 remains stationary relative to the drive disk 1.

[0072] It should be noted that when the center distance between the drive disk 1 and the intermittent disk 2 is appropriate, two of the sliders 21 on the intermittent disk 2 are simultaneously in contact with the arc surface 15. At this time, if the drive disk 1 is stationary, the intermittent disk 2 cannot rotate either.

[0073] Taking the figure as an example, when the channel 13 adopts the above structural design and the portion of the outer peripheral surface of the second cam portion 12 facing away from the channel 13 is an arc surface 15, during the transmission operation of the drive disk 1 and the intermittent disk 2, the running track of the slider 21 is approximately "heart"-shaped.

[0074] Now, in combination with the specific structure of the transmission device 100, taking the number of sliders 21 as 4 and respectively defined as slider A, slider B, slider C, and slider D as an example, the working principle and working process will be described. Specifically:

[0075] As Figure 6 shown, when the drive disk 1 rotates by an angle in the clockwise direction as shown in the figure, the slider A in the intermittent disk 2 starts to enter the opening (entrance) of the channel 13 on the drive disk 1, which is also the junction of the arc surface 15 on the drive disk 1 and the first arc segment 131 in the channel 13. That is to say, if the drive disk 1 continues to rotate in the clockwise direction, the slider A will start to enter the channel 13.

[0076] For the convenience of the following description, in the state shown Figure 6 the symmetry center line of the second cam portion 12 of the drive disk 1 is defined as the 0° position, and the radial line where the slider B in the intermittent disk 2 is located is defined as the 0° position.

[0077] As Figure 7As shown, when the drive disk 1 continues to rotate clockwise relative to the 0° position by α1°, the A slider in the intermittent disk 2 is driven by the limit of the channel 13 to rotate counterclockwise as shown in the figure, and the rotation angle is β1° relative to the 0° position. At this time, the D slider in the intermittent disk 2 starts to move away from the arc surface 15 of the second cam portion 12 due to the deflection of the intermittent disk 2. If the drive disk 1 stops rotating at this time, since the A slider is stuck in the channel 13, the intermittent disk 2 is also stationary and stuck, that is to say, whether the intermittent disk 2 rotates completely depends on whether the drive disk 1 is rotating, and it is completely controlled by the drive disk 1;

[0078] As Figure 8 shown, when the drive disk 1 continues to rotate clockwise to α2°, the intermittent disk 2 will rotate counterclockwise to the β2° position. At this time, the A slider starts to approach the pit of the direction-changing section 132, and the tooth-shaped portion 31 and the tooth groove portion 32 also start to approach;

[0079] As Figure 9 shown, when the drive disk 1 continues to rotate clockwise to α3°, the intermittent disk 2 rotates counterclockwise to the β3° position. At this time, the tooth-shaped portion 31 and the tooth groove portion 32 are already in contact and driving state. After that, the drive of the drive disk 1 on the intermittent disk 2 will be changed from driving the slider 21 by the channel 13 to meshing and driving the tooth-shaped portion 31 by the tooth groove portion 32. It should be emphasized here that there are two main purposes for setting the tooth-shaped portion 31 and the tooth groove portion 32 of the transfer member. One is to increase the accuracy of transmission, and the other is to improve the stability of transmission. Specifically, if there is no transfer member, when the drive disk 1 and the intermittent disk 2 are in the Figures 9 - 11 position shown, the slider 21 starts to approach and reach or leave the pit of the direction-changing section 132. Since the actual manufacturing dimension value of the width of the channel 13 is slightly larger than the outer diameter of the slider 21, there is a small gap between the two. In this way, near the pit of the direction-changing section 132, due to the turning and direction-changing of the direction-changing section 132, the constraint and limiting ability of the channel 13 on the slider 21 becomes weaker. At this time, if an external force shakes the intermittent disk 2, the intermittent disk 2 will shake significantly, which significantly reduces the movement accuracy of the intermittent disk 2. This is the first; second, near the pit of the direction-changing section 132, due to the turning and direction-changing of the direction-changing section 132, when the slider 21 passes through the pit during the movement, there will be a sudden change in the force direction, that is to say, the slider 21 moves from Figure 6After the entrance shown in the figure begins to enter the groove 13, the slider 21 is first subjected to the force of the first curved surface 1311 of the first arc segment 131 and rotates until the slider 21 reaches the pit of the direction-changing section 132. Thereafter, when the driving disk 1 continues to rotate clockwise, the slider 21 will begin to pass over the pit of the direction-changing section 132, and the second curved surface 1331 of the second arc segment 133 will drive the slider 21 to rotate the intermittent disk 2. That is to say, the force direction of the slider 21 at the pit of the direction-changing section 132 changes suddenly, which will produce a violent impact, especially under a large load. In this case, the driving disk 1 cannot perform a continuous and stable driving motion on the intermittent disk 2, and the characteristic structures such as the tooth-shaped portion 31 and the tooth groove portion 32 of the interface are provided to ensure that the driving disk 1 drives the intermittent disk 2 continuously and stably.

[0080] like Figure 10 , Figure 11 As shown, the driving disk 1 continues to rotate clockwise to the α4° position and the α5° position, and the intermittent disk 2 rotates counterclockwise to the β4° position and the β5° position. During this process, the tooth-shaped portion 31 and the tooth-groove portion 32 are always in contact and driving state until the tooth-shaped portion 31 and the tooth-groove portion 32 are separated from each other and reconnected to the groove 13 to drive the slider 21.

[0081] like Figure 12 As shown, the driving disc 1 continues to rotate clockwise to the α6° position, and the intermittent disc 2 rotates counterclockwise to the β6° position. At this time, the slider A in the intermittent disc 2 runs to another opening (exit) of the groove 13, which is also the junction of the arc surface 15 of the second cam portion 12 and the second arc segment 133. That is to say, if the driving disc 1 continues to rotate clockwise, the slider A will be free from the constraint and drive of the groove 13. At the same time, the bearing B on the intermittent disc 2 begins to fit onto the arc surface 15 of the second cam portion 12, thereby continuing to constrain and limit the free rotation of the intermittent disc 2.

[0082] like Figure 13 As shown, the drive disk 1 is composed of Figure 12 When the state shown in FIG. 1 continues to rotate in the clockwise direction, because there is no driving effect of the groove 13 on the slider 21, under the constraint and limit effect of the arc surface 15 on the slider A and the slider B, the intermittent disk 2 is stationary and does not rotate until the driving disk 1 rotates to the position shown in FIG. Figure 6 The body is in the position shown, and then the aforementioned action process is repeated, thereby realizing the transmission of driving the driving disk 1 to continuously rotate and drive the intermittent disk 2 to do intermittent motion.

[0083] like Figure 14As shown, a laver processing equipment 10 according to an embodiment of the present invention comprises a head claw chain assembly 6, a curtain frame 7, a large box feather chain 84 assembly 8, a transmission device 100 and a frame, wherein the head claw chain assembly 6 is used to convey the curtain frame 7, the curtain frame 7 can carry laver materials, and the large box feather chain 84 assembly 8 is connected with the head claw chain assembly 6 to transfer the curtain frame 7; the transmission device 100 is the transmission device 100 of any of the above embodiments, the first core shaft 4 of the transmission device 100 is transmission-connected to the large box feather chain 84 assembly 8, and the second core shaft 5 of the transmission device 100 is transmission-connected to the head claw chain assembly 6; the head claw chain assembly 6, the large box feather chain 84 assembly 8 and the transmission device 100 are all installed on the frame.

[0084] According to the laver processing equipment 10 of the embodiment of the present invention, the transmission device 100 is designed as a structure in which the groove 13, the slider 21 and the intersection assembly 3 cooperate with each other, which can not only make the rotation of the intermittent disk 2 completely controlled by the driving disk 1 to ensure the working reliability of the transmission device 100, but also enable the driving disk 1 to continuously and stably drive the intermittent disk 2 to perform intermittent motion. Therefore, compared with the related art, the laver processing equipment 10 using the transmission device 100 has improved operation smoothness and operation reliability, low operation noise, and can achieve the purpose of speeding up and increasing efficiency.

[0085] Specifically, the curtain frame 7 is not limited to a plane frame welded by steel bars. The curtain frame 7 is equipped with curtain pieces, which are laver material carriers in the production and processing of laver cake making, dehydration and drying. The first mandrel 4 and the second mandrel 5 in the transmission device 100 can be pivotally connected to the frame.

[0086] It should be noted that the laver processing equipment 10 is a complete set of equipment used to process the harvested fresh laver raw materials into dry laver sheets through operations such as cleaning, foreign matter sorting, chopping, concentration adjustment, cake making, cake dehydration, drying and shaping, sheet peeling, grading and packaging. For the main unit, it includes various functional sections such as curtain washing, cake making, water absorption, dehydration, curtain frame 7 handover, drying, and peeling. The mechanism action of the above-mentioned functional sections is completed by the joint drive of the machine head claw chain 63 and the large box feather chain 84, and there is a requirement for motion coordination between the machine head claw chain 63 and the large box feather chain 84 (that is, the feather chain 84 (baking box chain) of the laver processing unit performs continuous movement and drives the machine head claw chain 63 to perform intermittent movement at the same time) to accurately complete the handover of the curtain frame 7 components from the machine head to the large box and from the large box to the machine head.

[0087] like Figure 14As shown, in some embodiments, the head claw chain assembly 6 includes a first sprocket 61 and a second sprocket 62. The first sprocket 61 is pivotally connected to the frame. The second sprocket 62 is sleeved on the second mandrel 5 and is drivingly connected to the first sprocket 61 through a claw chain 63. In other words, the second sprocket 62 is coaxially and fixedly installed on the second mandrel 5. The second sprocket 62 can rotate together with the intermittent wheel. The claw chain 63 is sleeved on the second sprocket 62 and the first sprocket 61 to achieve the driving effect between the two.

[0088] As Figure 14 shown, in some embodiments, the head claw chain assembly 6 further includes a chain claw 64. The chain claw 64 is installed on the claw chain 63 and is adapted to be clamped to the curtain rack 7. That is, the chain claw 64 is used to clamp the curtain rack 7 to drive the curtain rack 7 to make a displacement movement, ensuring the transportation reliability of the curtain rack 7. There are multiple chain claws 64, which are arranged at intervals along the conveying direction of the claw chain 63. The distance between any two adjacent chain claws 64 is greater than the length of the curtain rack 7.

[0089] As Figure 14 shown, in some embodiments, the laver processing equipment 10 further includes a third sprocket 91 and a fourth sprocket 92. The third sprocket 91 is sleeved on the first mandrel 4. The fourth sprocket 92 is pivotally installed on the frame and is drivingly connected to the third sprocket 91 through a transition chain 93. The fourth sprocket 92 is drivingly connected to the large box feather chain 84 assembly 8, so as to form a transition assembly by the cooperation of the third sprocket 91, the fourth sprocket 92 and the transition chain 93, transmit the continuous rotation of the first mandrel 4 to the large box feather chain 84 assembly 8, and drive the large box feather chain 84 assembly 8 to rotate synchronously.

[0090] As Figure 14 shown, in some embodiments, the large box feather chain 84 assembly 8 includes a fifth sprocket 81, a sixth sprocket 82 and a feather chain rod 83. The fifth sprocket 81 is coaxially connected to the fourth sprocket 92. The sixth sprocket 82 is pivotally installed on the frame and is drivingly connected to the fifth sprocket 81 through a feather chain 84. The feather chain rod 83 is installed on the feather chain 84 and protrudes from the feather chain 84. There are multiple feather chain rods 83, which are arranged at intervals along the conveying direction of the feather chain 84. The space between any two adjacent feather chain rods 83 and the feather chain 84 together defines a receiving groove 85 for accommodating the curtain rack 7, so as to receive the curtain rack 7 transmitted by the claw chain 63 and hand over the curtain rack 7 that has completed the drying operation on the feather chain 84 to the claw chain 63 again.

[0091] Specifically, the first sprocket 61 and the sixth sprocket 82 can be horizontally arranged close to each other in the left-right direction in the figure, so that when the curtain rack 7 moves leftward from the claw chain 63 and approaches the feather chain rod 83, it will gradually enter the receiving groove 85 (i.e., the V-shaped opening) formed by the adjacent feather chain rods 83.

[0092] Now, in combination with the specific structure of the laver processing equipment 10, its working principle and working process will be described. Specifically:

[0093] On the one hand: The driving disk 1 makes continuous clockwise rotation under the drive of an external power source. It drives the intermittent disk 2 to make intermittent counterclockwise movement through the channel 13 and the slider 21. That is to say, when the driving disk 1 rotates one full circle, it will drive the intermittent disk 2 to deflect by a certain angle and then remain stationary for a period of time, and this cycle repeats. As Figure 14 shown, within the range where the driving disk 1 rotates by an angle of α6°, the intermittent disk 2 will rotate counterclockwise to β6°. Then, during the process where the driving disk 1 continues to rotate the remaining 360° - α6°, the intermittent disk 2 remains stationary. Obviously, by changing the length of the channel 13, the size of the α6 angle can be changed, so as to make the intermittent disk 2 obtain different intermittent ratios, that is, the ratio of the movement period to the stop period, to meet the optimized design of the movement law of the laver processing unit. For the intermittent disk 2 with four heads (four sliders 21) shown in the figure, when the driving disk 1 rotates one full circle, the intermittent disk 2 rotates 90°; Figure 14 shown, within the range where the driving disk 1 rotates by an angle of α6°, the intermittent disk 2 will rotate counterclockwise to β6°. Then, during the process where the driving disk 1 continues to rotate the remaining 360° - α6°, the intermittent disk 2 remains stationary. Obviously, by changing the length of the channel 13, the size of the α6 angle can be changed, so as to make the intermittent disk 2 obtain different intermittent ratios, that is, the ratio of the movement period to the stop period, to meet the optimized design of the movement law of the laver processing unit. For the intermittent disk 2 with four heads (four sliders 21) shown in the figure, when the driving disk 1 rotates one full circle, the intermittent disk 2 rotates 90°; Figure 12 shown, within the range where the driving disk 1 rotates by an angle of α6°, the intermittent disk 2 will rotate counterclockwise to β6°. Then, during the process where the driving disk 1 continues to rotate the remaining 360° - α6°, the intermittent disk 2 remains stationary. Obviously, by changing the length of the channel 13, the size of the α6 angle can be changed, so as to make the intermittent disk 2 obtain different intermittent ratios, that is, the ratio of the movement period to the stop period, to meet the optimized design of the movement law of the laver processing unit. For the intermittent disk 2 with four heads (four sliders 21) shown in the figure, when the driving disk 1 rotates one full circle, the intermittent disk 2 rotates 90°;

[0094] On the other hand: The continuously rotating driving disk 1 drives the feather chain 84 to rotate or move through the third sprocket 91, the transition chain 93, the fourth sprocket 92, and the fifth sprocket 81. When used for a single-step unit, it is usually designed that when the driving disk 1 rotates one full circle, the feather chain rod 83 deflects by 1 working position, that is, when the driving disk 1 rotates one full circle, the handover of 1 curtain rack 7 is realized. When used for a double-step unit, it is usually designed that when the driving disk 1 rotates one full circle, the feather chain rod 83 deflects by 2 working positions, that is, when the driving disk 1 rotates one full circle, the handover of 2 curtain racks 7 is realized (only one curtain rack 7 enters between adjacent feather chain rods 83 each time);

[0095] On yet another hand: The intermittently moving intermittent disk 2 drives the claw chain 63 to make intermittent rotation (movement) through the first sprocket 61, and successively sends the curtain rack 7 into the inverted V-shaped opening formed by the feather chain rod 83, thereby realizing the handover process of the curtain rack 7 from the claw chain 63 to the feather chain 84. The aforementioned handover process is dynamic. That is to say, during the process where the curtain rack 7 enters the V-shaped opening of the feather chain rod 83, the feather chain 84 moves continuously, while the claw chain 63 moves intermittently, in order to meet the needs of operations such as cake making and dehydration in the laver processing unit. These operations must be carried out when the curtain rack 7 is stationary, and this is also the fundamental reason why the laver processing unit must use the intermittent transmission device 100.

[0096] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the present invention.

[0097] In addition, the terms "first" and "second" are only used for descriptive purposes and should not be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include at least one of such features. In the description of the present invention, the meaning of "a plurality" is at least two, such as two, three, etc., unless otherwise specifically and clearly defined.

[0098] In the present invention, unless otherwise clearly defined and limited, the terms "mounted", "connected", "coupled", "fixed", etc. should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be a mechanical connection, an electrical connection, or communicable with each other; it may be directly connected, or indirectly connected through an intermediate medium, and it may be the internal communication of two elements or the interaction relationship between two elements, unless otherwise clearly limited. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0099] In the present invention, unless otherwise clearly defined and limited, the first feature being "on" or "under" the second feature may be that the first and second features are in direct contact, or the first and second features are indirectly in contact through an intermediate medium. Moreover, the first feature being "above", "over" and "on top of" the second feature may be that the first feature is directly above or obliquely above the second feature, or merely indicates that the first feature has a higher horizontal height than the second feature. The first feature being "under", "beneath" and "underneath" the second feature may be that the first feature is directly below or obliquely below the second feature, or merely indicates that the first feature has a lower horizontal height than the second feature.

[0100] In the present invention, the terms "one embodiment", "some embodiments", "an example", "a specific example", or "some examples", etc., mean that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any one or more embodiments or examples in a suitable manner. In addition, without contradiction, those skilled in the art may combine and combine the different embodiments or examples described in this specification and the features of the different embodiments or examples.

[0101] Although the embodiments of the present invention have been shown and described above, it can be understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those of ordinary skill in the art can make changes, modifications, substitutions, and variations to the above embodiments within the scope of the present invention.

Claims

1. A transmission device, characterized in that: include: A driving plate, the driving plate can pivot around the axis of the first mandrel, the driving plate is provided with a first cam portion and a second cam portion, the first cam portion and the second cam portion are arranged at intervals along the radial direction of the first mandrel and form a groove of equal width, the groove comprises a first arc segment, a direction-changing segment and a second arc segment connected in sequence, the first arc segment has a first curved surface formed on the first cam portion, and the second arc segment has a second curved surface formed on the second cam portion; An intermittent disk, the intermittent disk is pivotable around the axis of a second mandrel, the axial direction of the second mandrel is consistent with the axial direction of the first mandrel, the intermittent disk is provided with a slider and has a first motion state and a second motion state, in the first motion state, the slider is in sliding cooperation with the first curved surface, in the second motion state, the slider is in sliding cooperation with the second curved surface; and The interfacing assembly comprises a tooth-shaped portion and a tooth-groove portion, one of the tooth-shaped portion and the tooth-groove portion is arranged on the second cam portion, and the other is arranged on the intermittent disk, and when the slider is located in the change-of-direction section, the tooth-shaped portion and the tooth-groove portion mesh for transmission.

2. The transmission device according to claim 1, characterized in that: The first arc segment and the second arc segment are mirror-symmetrical relative to a reference plane, the axis of the first core shaft coincides with the reference plane, and on a projection plane perpendicular to the axial direction of the first core shaft, the curvature of the projection of the first arc segment gradually increases in a direction from the first arc segment toward the turning segment.

3. The transmission device according to claim 2, characterized in that: The direction-changing section is arranged on the driving disk with the reference plane as the symmetric center, the direction-changing section is concave toward the first core shaft, and when the slider is slidably matched with the direction-changing section, the intermittent disk moves at a constant speed relative to the driving disk; Any one of the tooth-shaped portion and the tooth groove portion is arranged on the second cam portion with the reference plane as the symmetry center and is adjacent to a position of the direction-changing section that is closest to the first core shaft.

4. The transmission device according to claim 1, characterized in that: The slider is pivotally connected to the intermittent disk, and the outer contour of the cross section of the slider is circular.

5. The transmission device according to claim 1, characterized in that: The number of the sliders is N, N ≥ 2n, wherein n is an integer greater than or equal to 2, and all the sliders are arranged at equal intervals along the circumference of the intermittent disk; The tooth-shaped portion is arranged on the outer peripheral surface of the intermittent disk and extends along the radial direction of the second core shaft. The slider is located between the tooth-shaped portion and the second core shaft along the radial direction of the second core shaft. There are multiple tooth-shaped portions and they correspond to the sliders one by one.

6. The transmission device according to any one of claims 1 to 5, characterized in that: The driving disc is further provided with a ring body, wherein the ring body and the first cam portion are both located on the outer peripheral side of the second cam portion and are arranged at intervals along the circumference of the first core shaft; At least one of the ring body and the second cam portion has an arc surface, and the arc surface is cocentric with the first core shaft. The intermittent disk also has a static state, and the slider is slidably matched with the arc surface in the static state.

7. A laver processing device, characterized in that: include: A machine head claw chain assembly, a curtain frame and a large box feather chain assembly, wherein the machine head claw chain assembly is used to transport the curtain frame, the curtain frame can carry laver materials, and the large box feather chain assembly is connected with the machine head claw chain assembly to transport the curtain frame; A transmission device, wherein the transmission device is the transmission device according to any one of claims 1 to 6, wherein the first mandrel of the transmission device is transmission-connected to the large box feather chain assembly, and the second mandrel of the transmission device is transmission-connected to the head claw chain assembly; as well as The frame, the head claw chain assembly, the large box feather chain assembly and the transmission device are all installed on the frame.

8. The laver processing equipment according to claim 7, characterized in that: The machine head claw chain assembly comprises: A first sprocket and a second sprocket, wherein the first sprocket is pivotally connected to the frame, and the second sprocket is sleeved on the second spindle and drivingly connected to the first sprocket via a claw chain; and / or A chain claw is installed on the claw chain and is suitable for clamping the curtain frame. There are multiple chain claws and they are arranged at intervals along the conveying direction of the claw chain. The distance between any two adjacent chain claws is greater than the length of the curtain frame.

9. The laver processing equipment according to claim 7 or 8, characterized in that: It also includes a third sprocket and a fourth sprocket, wherein the third sprocket is sleeved on the first core shaft, the fourth sprocket is pivotally mounted on the frame and is drivingly connected to the third sprocket via a transition chain, and the fourth sprocket is drivingly connected to the large box feather chain assembly.

10. The laver processing equipment according to claim 9, characterized in that: The large box feather chain assembly includes: a fifth sprocket and a sixth sprocket, wherein the fifth sprocket is coaxially connected to the fourth sprocket, and the sixth sprocket is pivotally mounted on the frame and drivingly connected to the fifth sprocket via a feather chain; and A feather chain rod is installed on the feather chain and protrudes from the feather chain. There are a plurality of feather chain rods and they are arranged at intervals along the conveying direction of the feather chain. Any two adjacent feather chain rods and the feather chain jointly define a receiving groove for receiving the curtain frame.

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