Transmission device and laver processing equipment

Abstract

The utility model 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 utility model relates to transmission device technical field especially relates to a transmission device and laminaria processing equipment. BACKGROUND

[0002] The machine head claw chain in laminaria processing unit is intermittent motion, and the big box feather chain is continuous motion, in order to accurately complete the handover of curtain frame parts between the machine head and the big box, the intermittent transmission device is needed to ensure the motion cooperation between the machine head claw chain and the big box feather chain.

[0003] However, the intermittent transmission device in the related art, the intermittent motion law is often parabolic when starting from zero speed to the highest speed and stopping from zero speed, when the laminaria processing unit moves at a high speed (that is, at a faster intermittent frequency), the running speed of the curtain frame is too fast near the highest speed point, and the prefabricated laminaria cake on the curtain frame is prone to dispersion due to shaking, resulting in the decline of the overall operation stability and work reliability of the laminaria processing unit, thereby restricting the speed increase and efficiency improvement of the laminaria processing unit. SUMMARY

[0004] The utility model aims at at least one of the technical problems in the related art to some extent.

[0005] Therefore, the embodiment of the utility model provides a transmission device, which can run stably, has a simple overall structure and strong work reliability.

[0006] The embodiment of the utility model provides a laminaria processing equipment.

[0007] According to the transmission device provided by the embodiment of the utility model, the driving disc, the intermittent disc and the handover assembly are provided, the driving disc is pivotable around the axis of the first core shaft, the first cam part and the second cam part are arranged on the driving disc, the first cam part and the second cam part are arranged along the radial direction of the first core shaft and form the equal-width channel, the channel comprises the first arc segment, the direction-changing segment and the second arc segment connected in sequence, the first arc segment has the first curved surface formed on the first cam part, and the second arc segment has the second curved surface formed on the second cam part, the intermittent disc is pivotable around the axis of the second core shaft, the axis direction of the second core shaft is consistent with the axis direction of the first core shaft, the intermittent disc is provided with the sliding block and has the first motion state and the second motion state, in the first motion state, the sliding block is in sliding cooperation with the first curved surface, in the second motion state, the sliding block is in sliding cooperation with the second curved surface, the handover assembly comprises the tooth type part and the tooth groove part, one of the tooth type part and the tooth groove part is arranged on the second cam part, and the other is arranged on the intermittent disc, when the sliding block is located in the direction-changing segment, the tooth type part and the tooth groove part are in meshing transmission.

[0008] According to the embodiment of the utility model, the first core shaft can drive the driving disc to rotate, so that the sliding block on the intermittent disc can slide along the groove, in this process, the sliding block is first subjected to the force of the first curved surface after entering the groove, the intermittent disc is in the first motion state and rotates around the second core shaft, then, the sliding block slides to the turning section, the force direction of the sliding block will change in the turning section, that is, the force acting on the sliding block is switched from the first curved surface to the second curved surface, so that the intermittent disc is in the second motion state when the sliding block is subjected to the force of the second curved surface, wherein the groove can constrain and limit the sliding block, so that the rotation of the intermittent disc is completely controlled by the driving disc, avoiding the problem that the intermittent disc may self-rotate due to accidental shutdown, resulting in misalignment interference or mutual damage of machine parts, but in the turning section, the constraint and limiting ability of the groove on the sliding block will be weakened, at this time, if the intermittent disc is shaken by external force, the intermittent disc will shake obviously, resulting in a decrease in the motion accuracy of the transmission device, and the handover assembly can increase the accuracy of transmission and reduce the sudden change of the force direction on the sliding block when the sliding block passes through the turning section, effectively preventing the damage risk of the sliding block under heavy load, improving the stability of transmission, ensuring the continuous, reliable and stable driving of the driving disc on the intermittent disc, so compared with the related art, the utility model can run stably, the overall structure is simple, and the working reliability is high.

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

[0010] In some embodiments, the turning section is disposed on the driving disc with the reference plane as a symmetric center, the turning section is concave to the first core shaft, and when the sliding block is slidingly fitted in the turning section, the intermittent disc moves at a constant speed relative to the driving disc.

[0011] Any one of the tooth-shaped part and the tooth groove part is disposed on the second cam part with the reference plane as a symmetric center and adjacent to a position closest to the first core shaft of the turning section.

[0012] In some embodiments, the sliding block is pivotably connected to the intermittent disc, and an outer contour of a cross section of the sliding block is circular.

[0013] In some embodiments, the number of the sliding blocks is N, N≥2n, wherein n is an integer greater than or equal to 2, and all the sliding blocks are arranged at equal intervals along a circumferential direction of the intermittent disc.

[0014] The toothed portion is disposed on the outer peripheral surface of the intermittent disk and extends radially along the second spindle. The slider is located radially between the toothed portion and the second spindle. There are multiple toothed portions, each corresponding to a slider.

[0015] In some embodiments, the drive 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 circumferential intervals along the first spindle;

[0016] At least one of the ring body and the second cam portion has an arc surface, the arc surface is concentric with the first mandrel, the intermittent disk also has a stationary state, and the slider slides in the stationary state with the arc surface.

[0017] A seaweed processing device according to an embodiment of the present invention includes a head claw chain assembly, a curtain frame, a large box feather chain assembly, a transmission device, and a frame. The head claw chain assembly is used to transport the curtain frame, which can carry seaweed material. The large box feather chain assembly is connected to the head claw chain assembly to transfer the curtain frame. The transmission device is the transmission device described in any of the above embodiments. The first spindle of the transmission device is drivenly connected to the large box feather chain assembly, and the second spindle of the transmission device is drivenly connected to the head claw chain assembly. The head claw chain assembly, the large box feather chain assembly, and the transmission device are all mounted on the frame.

[0018] According to the embodiment of the present invention, the seaweed processing equipment has a transmission device designed as a structure in which a channel, a slider, and a connecting component cooperate. This not only allows the rotation of the intermittent disk to be completely controlled by the drive disk to ensure the reliability of the transmission device, but also enables the drive disk to continuously and stably drive the intermittent disk to perform intermittent motion. Therefore, compared with related technologies, the seaweed processing equipment using this transmission device has improved operational stability and reliability, low operating noise, and can achieve the purpose of speed increase and efficiency improvement.

[0019] In some embodiments, the machine head claw chain assembly includes a first sprocket and a second sprocket, the first sprocket being pivotally connected to the frame, and the second sprocket being sleeved on the second spindle and drivenly connected to the first sprocket via a claw chain.

[0020] In some embodiments, the machine head claw chain assembly further includes chain claws, which are mounted on the claw chain and adapted to engage the curtain frame. There are multiple chain claws arranged at intervals along the conveying direction of the claw chain, and the distance between any two adjacent chain claws is greater than the length of the curtain frame.

[0021] In some embodiments, the seaweed processing equipment further includes a third sprocket and a fourth sprocket. The third sprocket is sleeved on the first spindle, and the fourth sprocket is pivotally mounted on the frame and drivenly connected to the third sprocket via a transition chain. The fourth sprocket is drivenly connected to 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, and the sixth sprocket is pivotally mounted on the frame and drivenly connected to the fifth sprocket via the feather chain. The feather chain rods are mounted on the feather chain and protrude from the feather chain. There are multiple feather chain rods arranged at intervals along the conveying direction of the feather chain, and any two adjacent feather chain rods and the feather chain together define a receiving groove for accommodating the curtain frame.

[0023] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0024] Figure 1 This is a schematic diagram of the transmission device according to an embodiment of the present utility model.

[0025] Figure 2 This is a schematic diagram of the first structure of the drive disc in the transmission device according to an embodiment of the present utility model.

[0026] Figure 3 This is a schematic diagram of a second structure of the drive disc in the transmission device according to an embodiment of the present utility model.

[0027] Figure 4 This is a schematic diagram of the third structure of the drive disc in the transmission device according to an embodiment of the present utility model.

[0028] Figure 5 This is a schematic diagram of the intermittent disc in the transmission device according to an embodiment of the present utility model.

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

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

[0031] Figure 8 This is a schematic diagram of the transmission device according to an embodiment of the present invention, showing the intermittent disc switching from a first motion state to a second motion state, and the slider cooperating with the direction-changing section. Figure 1 .

[0032] Figure 9 This is a schematic diagram of the transmission device according to an embodiment of the present invention, showing the intermittent disc switching from a first motion state to a second motion state, and the slider cooperating with the direction-changing section. Figure 2 .

[0033] Figure 10 This is a schematic diagram of the transmission device according to an embodiment of the present invention, showing the intermittent disc switching from a first motion state to a second motion state, and the slider cooperating with the direction-changing section. Figure 3 .

[0034] Figure 11 This is a schematic diagram of the transmission device according to an embodiment of the present invention, showing the intermittent disc switching from a first motion state to a second motion state, and the slider cooperating with the direction-changing section. Figure 4 .

[0035] Figure 12 This is a schematic diagram of the structure of the transmission device according to an embodiment of the present invention, in which the intermittent disc is in the second motion state and the slider is at the outlet of the channel.

[0036] Figure 13 This is a schematic diagram of the structure of the transmission device according to an embodiment of the present invention when the intermittent disc is in a stationary state.

[0037] Figure 14 This is a schematic diagram of the structure of a seaweed processing device according to an embodiment of the present utility model.

[0038] Figure label:

[0039] 10. Laver processing equipment;

[0040] 100. Transmission device;

[0041] 1. Drive disc; 11. First cam section; 12. Second cam section; 13. Channel; 131. First arc segment; 1311. First curved surface; 132. Directional section; 133. Second arc segment; 1331. Second curved surface; 14. Ring body; 15. Circular arc surface;

[0042] 2. Intermittent disk; 21. Slider;

[0043] 3. Interchange assembly; 31. Toothed section; 32. Toothed groove section;

[0044] 4. First mandrel;

[0045] 5. Second mandrel;

[0046] 6. Head claw chain assembly; 61. First sprocket; 62. Second sprocket; 63. Claw chain; 64. Chain claw;

[0047] 7. Curtain frame;

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

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

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

[0051] like Figures 1 to 5 As shown, a transmission device 100 according to an embodiment of the present invention includes a drive disk 1, an intermittent disk 2, and a transfer assembly 3. The drive disk 1 is pivotable about the axis of a first spindle 4. The drive 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 radially at intervals along the first spindle 4 and form a channel 13 of equal width. The channel 13 includes a first arc segment 131, a reversing segment 132, and a second arc segment 133 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 1311 formed on the second cam portion 12. The intermittent disk 2 is pivotable about the axis of the second spindle 5, which is aligned with the axis of the first spindle 4. The intermittent disk 2 has a slider 21 and two motion states. In the first motion state, the slider 21 slides against the first curved surface 1311; in the second motion state, the slider 21 slides against the second curved surface 1331. In other words, when the intermittent disk 2 is in the first motion state, the slider 21 rotates due to the force exerted by the first curved surface 1311; and when the intermittent disk 2 is in the second motion state, the slider 21 rotates due to the force exerted by the second curved surface 1331. The connecting assembly 3 includes a toothed portion 31 and a toothed portion 32. One of the toothed portion 31 and the toothed portion 32 is located on the second cam portion 12, and the other is located on the intermittent disk 2. When the slider 21 is located in the reversing section 132, the toothed portion 31 and the toothed portion 32 mesh and drive, causing the intermittent disk 2 to switch from the first motion state to the second motion state.

[0052] According to the transmission device 100 of this utility model embodiment, the first spindle 4 can drive the drive disk 1 to rotate, so that the slider 21 on the intermittent disk 2 can slide along the channel 13. During this process, after the slider 21 enters the channel 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 spindle 5. Then, the slider 21 slides to the reversing section 132, and the force direction of the slider 21 will change in the reversing section 132. That is, the force acting on the slider 21 switches from the first curved surface 1311 to the second curved surface 1331, so that when the slider 21 is subjected to the force of the second curved surface 1331, the intermittent disk 2 is in a second motion state and rotates. The channel 13 can constrain and limit the slider 21, so that the rotation of the intermittent disk 2 is completely controlled by the drive disk 1, and avoids accidental stop. The intermittent disk 2 may rotate, causing misalignment, interference, or mutual damage to the machine parts. However, in the reversing section 132, the constraint and limiting ability of the channel 13 on the slider 21 will weaken. At this time, if the intermittent disk 2 is shaken by external force, the intermittent disk 2 will wobble significantly, thereby reducing the motion accuracy of the transmission device 100. The transfer component 3 can increase the accuracy of the transmission through the meshing transmission between the toothed part 31 and the toothed groove part 32 when the slider 21 passes through the reversing section 132, and reduce the violent impact of the sudden change in the force direction on the slider 21. This effectively prevents the risk of damage to the slider 21 under heavy load, improves the stability of the transmission, and ensures the continuous, reliable, and stable drive of the drive disk 1 on the intermittent disk 2. Therefore, compared with related technologies, this utility model can operate smoothly, has a simple overall structure, and has high working reliability.

[0053] It is understandable that "drive disk 1 is pivotable about the axis of the first spindle 4," meaning that drive disk 1 is mounted on the first spindle 4, and when the first spindle 4 is rotated by a driver or manually, drive disk 1 will rotate synchronously. Similarly, "intermittent disk 2 is pivotable about the axis of the second spindle 5," meaning that intermittent disk 2 is mounted on the second spindle 5, and when intermittent disk 2 is driven to rotate by drive disk 1, the second spindle 5 can rotate synchronously.

[0054] In addition, in some embodiments of the present invention, the toothed portion 31 is provided on the second cam portion 12 and the toothed portion 32 is provided on the intermittent disk 2; in other embodiments, the toothed portion 32 is provided on the second cam portion 12 and the toothed portion 31 is provided on the intermittent disk 2. Therefore, the arrangement of the handover component 3 of the present invention can be the two methods mentioned above.

[0055] Specifically, the drive disk 1 can be coaxially connected to the first spindle 4, that is, a first through hole extending along its thickness direction can be opened in the center of the drive disk 1, and the first spindle 4 can be coaxially fixedly installed in the first through hole, so as to facilitate the drive disk 1 to rotate by a driver or manually. The width of the channel 13 is equal to or slightly larger than the size of the slider 21, so that the slider 21 can be slidably constrained by the channel 13. The channel 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 direction-changing segment 132, and the outlet is located at the end of the second arc segment 133 away from the direction-changing segment 132. When the drive disk 1 rotates, the slider 21 can enter the channel 13 from the inlet and leave the constraint and drive of the channel 13 from the outlet. The first arc segment 131, the direction-changing segment 132 and the second arc segment 133 are arranged sequentially along the extension direction of the channel 13. The intermittent disk 2 can be coaxially connected to the second spindle 5, that is, a second through hole extending along its thickness direction can be opened in the center of the intermittent disk 2, and the second spindle 5 can be coaxially fixedly installed in the second through hole. The first spindle 4 and the second spindle 5 are arranged radially spaced along the first spindle 4. The toothed portion 32 can be a mounting block with toothed grooves, such as the toothed portion 32 can be fixed to the second cam portion 12 by bolts, or the toothed 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 with respect to the reference plane, the axis of the first mandrel 4 coincides with the reference plane, and on the projection plane perpendicular to the axis of the first mandrel 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 is understandable that, since the first arc segment 131 and the second arc segment 133 are arranged in a mirror symmetrical manner, when the curvature of the projection of the first arc segment 131 gradually increases along 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 along the direction from the turning segment 132 toward the second arc segment 133. This allows the sliding speed of the slider 21 to gradually increase from zero speed in the first arc segment 131 and gradually decrease to zero speed in the second arc segment 133 when the drive disk 1 rotates and the slider 21 slides along the channel 13.

[0058] Meanwhile, designing the first arc segment 131 and the second arc segment 133 as a mirror symmetric structure is also beneficial to the processing and forming of the channel 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 reversing segment 132 is arranged on the drive disk 1 with the reference plane as the center of symmetry. The reversing segment 132 is concave towards the first spindle 4. In other words, on the projection plane perpendicular to the first spindle 4, the projection of the reversing segment 132 is a mirror-symmetrical concave structure. When the slider slides into the reversing segment, the intermittent disk moves at the same speed relative to the drive disk. At this time, on the projection plane perpendicular to the first spindle 4, the curvature of the projection of the reversing segment 132 gradually increases and then gradually decreases. That is, the curvature of the projection of the reversing segment 132 gradually increases along the direction from the first arc segment 131 toward the position closest to the first spindle 4, and gradually decreases along the direction from the position closest to the first spindle 4 toward the second arc segment 133, so as to minimize the impact of the abrupt change in shape of the reversing segment 132 on the smooth sliding of the slider 21. The minimum curvature of the projection of the reversing segment 132 is equal to the maximum curvature of the projection of the first arc segment 131.

[0060] It is understandable that, combining the structural design of the first arc segment 131 and the second arc segment 133, and designing the curvature of the projection of the direction-changing segment 132 to gradually increase and then gradually decrease, so that when the drive disk 1 rotates, the intermittent disk 2 can achieve the motion law of starting from zero and accelerating (i.e., the first arc segment 131 is the acceleration segment) - running at a constant speed (i.e., the direction-changing segment 132 is the constant speed segment) - decelerating and stopping (i.e., the second arc segment 133 is the deceleration segment). At this time, the slider 21 can move at the highest speed at a constant speed in the direction-changing segment 132.

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

[0062] In addition, by adjusting the extension length of each of the first arc segment 131, the reversing segment 132, and the second arc segment 133, the movement duration of the intermittent disc 2 in the acceleration segment, the constant speed segment, and the deceleration segment can be changed, so that when the transmission device 100 is applied to the seaweed processing unit, it is beneficial to increase the speed and efficiency of the seaweed processing unit.

[0063] Either the toothed portion 31 or the toothed portion 32 is arranged on the second cam portion 12 with the reference plane as the center of symmetry and is located near the position closest to the first spindle 4 of the deflection section 132. That is, the toothed portion 31 or the toothed portion 32 is also a mirror symmetrical structure and corresponds to the recess of the deflection section 132. In other words, the toothed portion 31 or the toothed portion 32 is arranged in the middle position near the deflection section 132.

[0064] It is understandable that the above-mentioned structural design of the deflection section 132 can further simplify the structure of the channel 13 and facilitate the processing and forming of the channel 13.

[0065] It should be noted that the transfer component 3 mainly serves as a transition and connection near the middle position of the reversing section 132 to prevent severe impact on the slider 21 caused by the abrupt change in shape. The effective range of the reversing section 132 on the slider 21 is greater than that of the transfer component 3. In addition, to prevent over-positioning or interference of the drive, the gap at the position on the reversing section 132 corresponding to the effective range of the transfer component 3 can be slightly enlarged, which means that the width of the channel 13 at that position is slightly larger, so that only the transfer component 3 drives the slider 21 at that 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 channel 13 and reduce wear on the slider 21.

[0067] For example, the slider 21 is not limited to a cylindrical slider 21, such as a bearing, so that the outer peripheral surface of the slider 21 makes rolling contact with the channel 13, in which case the width of the channel 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, where N ≥ 2n, and 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; other unlisted values ​​within this range also apply. 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 peripheral surface of the intermittent disk 2 and extends radially along the second spindle 5. The slider 21 is located radially between the toothed portion 31 and the second spindle 5. In other words, on the projection plane perpendicular to the axial direction of the second spindle 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 spindle 5, and the slider 21 is closer to the second spindle 5 than the toothed portion 31. For example, the toothed portion 31 is formed on the outer peripheral surface 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, each corresponding to a slider 21, 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. The ring body 14 and the first cam portion 11 are both located on the outer periphery of the second cam portion 12 and are arranged at intervals along the circumference of the first spindle 4. At this time, the inner peripheral surface of the first cam portion 11 and the outer peripheral surface of the second cam portion 12 together form a channel 13.

[0071] At least one of the ring body 14 and the second cam portion 12 has an arc surface 15. That is, in some embodiments of the present invention, the ring body 14 has an arc surface 15; in other embodiments, the second cam portion 12 has an arc surface 15; and in still other embodiments, both the ring body 14 and the second cam portion 12 have arc surfaces 15. Therefore, the arc surface 15 of the present invention can be provided in the aforementioned three ways. The arc surface 15 is concentric with the first spindle 4. The intermittent disk 2 also has a stationary state. The slider 21 slides with the arc surface 15 in the stationary state. In other words, when the slider 21 slides 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 abutting against the arc surface 15. At this time, if the drive disk 1 is stationary, the intermittent disk 2 will also be unable to rotate.

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

[0074] Now, taking the specific structure of the transmission device 100 as an example, with four sliders 21 designated as slider A, slider B, slider C, and slider D, its working principle and process will be explained as follows:

[0075] like Figure 6 As shown, when the drive disk 1 rotates clockwise at an angle as shown in the figure, slider A in the intermittent disk 2 begins to enter the opening (entrance) of the channel 13 on the drive disk 1. This is also the junction of the arc surface 15 on the drive disk 1 and the first arc segment 131 in the channel 13. In other words, if the drive disk 1 continues to rotate clockwise, slider A will begin to enter the channel 13.

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

[0077] like Figure 7As shown, when the drive disk 1 continues to rotate clockwise by α1° relative to the 0° position, the A slider in the intermittent disk 2 is driven by the limiting drive of the channel 13 to rotate counterclockwise as shown in the figure, with a rotation angle of β1° relative to the 0° position. At this time, the D slider in the intermittent disk 2 begins to move away from the arc surface 15 of the second cam part 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 depends entirely on whether the drive disk 1 is rotating, and it is completely controlled by the drive disk 1.

[0078] like Figure 8 As shown, when the drive disk 1 continues to rotate clockwise to α2°, the intermittent disk 2 will rotate counterclockwise to β2°. At this time, the A slider begins to approach the recess of the reversing section 132, and the toothed part 31 and the toothed part 32 also begin to approach each other.

[0079] like Figure 9 As shown, when the drive disk 1 continues to rotate clockwise to position α3°, the intermittent disk 2 rotates counterclockwise to position β3°. At this point, the toothed portion 31 and the toothed portion 32 are in contact and driving state. Afterward, the drive of the intermittent disk 2 by the drive disk 1 will change from the channel 13 driving the slider 21 to the toothed portion 32 engaging and driving the toothed portion 31. It is important to note that the toothed portion 31 and the toothed portion 32 of the connecting part have two main purposes: first, to increase the accuracy of the transmission; and second, to improve the stability of the transmission. Specifically, if there were no connecting part, when the drive disk 1 and the intermittent disk 2 are in contact... Figures 9-11 At the indicated position, slider 21 begins to approach and reach or leave the recess of the deflection section 132. Since the actual manufacturing dimensions of the channel 13 width are slightly larger than the outer diameter of slider 21, there is a small gap between them. Therefore, near the recess of the deflection section 132, due to the turning and changing direction of the deflection section 132, the constraint and limiting ability of the channel 13 on slider 21 weakens. If an external force is applied to shake the intermittent disk 2 at this time, the intermittent disk 2 will wobble significantly, which obviously reduces the motion accuracy of the intermittent disk 2. Secondly, near the recess of the deflection section 132, due to the turning and changing direction of the deflection section 132, when slider 21 passes through this recess during its movement, a sudden change in the direction of force will occur. That is to say, slider 21 from... Figure 6After the inlet shown enters the channel 13, the slider 21 is first rotated by the force of the first curved surface 1311 of the first arc segment 131 until the slider 21 reaches the recess of the reversing segment 132. After that, when the drive disk 1 continues to rotate clockwise, the slider 21 will begin to pass the recess of the reversing segment 132. Then, the second curved surface 1331 of the second arc segment 133 drives the slider 21 to rotate the intermittent disk 2. That is to say, the force direction of the slider 21 changes suddenly at the recess of the reversing segment 132, which will produce a violent impact, especially under heavy load. In this case, the drive disk 1 cannot make a continuous and stable driving motion on the intermittent disk 2. The toothed part 31 and the toothed groove part 32 of the connecting part are designed to ensure the continuous and stable driving of the intermittent disk 2 by the drive disk 1.

[0080] like Figure 10 , Figure 11 As shown, the drive disk 1 continues to rotate clockwise to the α4° and α5° positions, and the intermittent disk 2 rotates counterclockwise to the β4° and β5° positions. During this process, the toothed part 31 and the toothed part 32 are always in contact and driving state until the toothed part 31 and the toothed part 32 disengage from each other and are re-transferred to the channel 13 to drive the slider 21.

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

[0082] like Figure 13 As shown, drive disk 1 is composed of Figure 12 When the state shown continues to rotate clockwise, because there is no longer a driving force of the channel 13 on the slider 21, and under the constraint and limiting effect of the arc surface 15 on sliders A and B, the intermittent disk 2 remains stationary until the driving disk 1 rotates to the position shown. Figure 6 The body position is shown, and then the aforementioned action process is repeated, thereby realizing the transmission that drives the continuous rotation of the drive disk 1 while driving the intermittent disk 2 to perform intermittent motion.

[0083] like Figure 14As shown, a seaweed processing device 10 according to an embodiment of the present invention includes a head claw chain assembly 6, a curtain frame 7, a large box feather chain assembly 84, a transmission device 100, and a frame. The head claw chain assembly 6 is used to transport the curtain frame 7, which can carry seaweed material. The large box feather chain assembly 84 is connected to 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 spindle 4 of the transmission device 100 is connected to the large box feather chain assembly 84, and the second spindle 5 of the transmission device 100 is connected to the head claw chain assembly 6. The head claw chain assembly 6, the large box feather chain assembly 84, and the transmission device 100 are all mounted on the frame.

[0084] According to the embodiment of the present invention, the seaweed processing equipment 10 is designed with a structure in which the transmission device 100, the slide block 21, and the connecting component 3 cooperate. This not only allows the rotation of the intermittent disk 2 to be completely controlled by the drive disk 1 to ensure the working reliability of the transmission device 100, but also enables the drive disk 1 to continuously and stably drive the intermittent disk 2 to perform intermittent motion. Therefore, compared with related technologies, the seaweed processing equipment 10 using this transmission device 100 has improved running stability and reliability, low operating noise, and can achieve the purpose of speed increase and efficiency improvement.

[0085] Specifically, the curtain frame 7 is not limited to a planar frame welded with steel bars. Curtains are installed on the curtain frame 7, and these curtains serve as carriers for the seaweed material during the production and processing of seaweed, such as seaweed cake making, dehydration, and drying. Both the first spindle 4 and the second spindle 5 in the transmission device 100 can be pivotally connected to the frame.

[0086] It should be noted that the seaweed processing equipment 10 is a complete set of equipment used to process freshly harvested seaweed raw materials into dried seaweed sheets through processes such as washing, foreign object sorting, chopping, concentration adjustment, cake making, cake dehydration, drying and shaping, sheet peeling, grading and packaging. For the main unit, it includes functional sections such as washing curtain, cake making, water absorption, dehydration, curtain 7 handover, drying, and seaweed peeling. The mechanical actions of the aforementioned functional sections are completed by the combined drive of the machine head claw chain 63 and the large box feather chain 84. Moreover, there is a requirement for motion coordination between the machine head claw chain 63 and the large box feather chain 84 (i.e., the feather chain 84 (drying box chain) of the seaweed processing unit makes continuous movement, while driving the machine head claw chain 63 to make intermittent movement), so as to accurately complete the handover of the curtain 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 machine 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, and the second sprocket 62 is sleeved on the second spindle 5 and is connected to the first sprocket 61 via a claw chain 63. In other words, the second sprocket 62 is coaxially fixedly installed on the second spindle 5 and can rotate together with the intermittent wheel. The claw chain 63 is sleeved on the second sprocket 62 and the first sprocket 61 to realize the transmission between the two.

[0088] like Figure 14 As shown, in some embodiments, the machine head claw chain assembly 6 further includes chain claws 64. The chain claws 64 are mounted on the claw chain 63 and are adapted to engage the curtain frame 7. That is, the chain claws 64 are used to hold the curtain frame 7 to drive the curtain frame 7 to make displacement movements, ensuring the reliability of the transport of the curtain frame 7. There are multiple chain claws 64, which are arranged at intervals along the conveying direction of the claw chain 63, and the distance between any two adjacent chain claws 64 is greater than the length of the curtain frame 7.

[0089] like Figure 14 As shown, in some embodiments, the seaweed processing equipment 10 further includes a third sprocket 91 and a fourth sprocket 92. The third sprocket 91 is sleeved on the first spindle 4, and the fourth sprocket 92 is pivotally mounted on the frame and is connected to the third sprocket 91 via a transition chain 93. The fourth sprocket 92 is connected to the large box feather chain 84 assembly 8, so that the third sprocket 91, the fourth sprocket 92 and the transition chain 93 cooperate to form a transition assembly, which transmits the continuous rotation of the first spindle 4 to the large box feather chain 84 assembly 8, so as to drive the large box feather chain 84 assembly 8 to rotate synchronously.

[0090] like Figure 14 As 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 mounted on the frame and is connected to the fifth sprocket 81 via the feather chain 84. The feather chain rod 83 is mounted on the feather chain 84 and protrudes from the feather chain 84. There are multiple feather chain rods 83, which are spaced apart along the conveying direction of the feather chain 84. Any two adjacent feather chain rods 83 and the feather chain 84 together define a receiving groove 85 for accommodating the curtain frame 7, so as to receive the curtain frame 7 driven by the claw chain 63, and to transfer the curtain frame 7 that has been dried on the feather chain 84 back to the claw chain 63.

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

[0092] The working principle and process of this seaweed processing equipment 10 will now be explained in detail, based on its specific structure:

[0093] On the one hand: Drive disk 1 performs actions under the drive of external power, such as Figure 14 The continuous clockwise rotation shown drives the intermittent disk 2 to perform the following actions via the channel 13 and slider 21: Figure 14 The intermittent counter-clockwise movement shown means that as drive disc 1 rotates one revolution, drive intermittent disc 2 to deflect at a certain angle, then remain stationary for a period of time, and this cycle repeats. Figure 12 As shown, when the drive disk 1 rotates within the α6° angle range, the intermittent disk 2 will rotate counterclockwise to β6°. Then, during the remaining 360°-α6° rotation of the drive disk 1, the intermittent disk 2 remains stationary. Clearly, by changing the length of the channel 13, the size of the α6 angle can be changed, allowing the intermittent disk 2 to achieve different intermittent ratios, i.e., the ratio of the moving period to the stationary period, thus satisfying the optimized design of the motion law of the seaweed processing unit. For the four-head (four sliders 21) intermittent disk 2 shown in the figure, for every revolution of the drive disk 1, the intermittent disk 2 rotates 90°.

[0094] On the other hand, the continuously rotating drive disc 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 in a single stepper unit, it is usually designed so that when the drive disc 1 rotates one revolution, the feather chain rod 83 deflects one working position, that is, when the drive disc 1 rotates one revolution, one curtain frame 7 is connected. When used in a double stepper unit, it is usually designed so that when the drive disc 1 rotates one revolution, the feather chain rod 83 deflects two working positions, that is, when the drive disc 1 rotates one revolution, two curtain frames 7 are connected (adjacent feather chain rods 83 only run into one curtain frame 7 at a time).

[0095] On another front: the intermittently moving disc 2 drives the claw chain 63 to rotate (move) intermittently via the first sprocket 61, sequentially feeding the curtain frame 7 into the inverted V-shaped opening formed by the feather chain rod 83, thus realizing the transfer process of the curtain frame 7 from the claw chain 63 to the feather chain 84. The aforementioned transfer process is dynamic, that is, during the process of the curtain frame 7 entering the V-shaped opening of the feather chain rod 83, the feather chain 84 moves continuously, while the claw chain 63 moves intermittently. This is to meet the needs of the laver processing unit for operations such as cake making and dehydration. These operations can only be carried out when the curtain frame 7 is stationary, which is the fundamental reason why the laver processing unit must use the intermittent transmission device 100.

[0096] In the description of this utility model, it should be understood that 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., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0097] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this utility model, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0098] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0099] In this utility model, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0100] In this utility model, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of this utility model. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0101] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled 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 drive disk, which is pivotable about the axis of a first spindle, is provided with a first cam portion and a second cam portion. The first cam portion and the second cam portion are arranged radially at intervals along the first spindle and form a channel of equal width. The channel includes a first arc segment, a reversing 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 is pivotable about the axis of a second spindle, the axis of which is consistent with the axis of the first spindle. 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 slides with the first curved surface, and in the second motion state, the slider slides with the second curved surface. and The transfer assembly includes a toothed portion and a toothed portion, one of which is disposed on the second cam portion and the other is disposed on the intermittent disk. When the slider is located in the reversing section, the toothed portion and the toothed portion engage 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 with respect to the reference plane. The axis of the first mandrel coincides with the reference plane. On the projection plane perpendicular to the axis of the first mandrel, the curvature of the projection of the first arc segment gradually increases from the first arc segment toward the turning segment.

3. The transmission device according to claim 2, characterized in that, The reversing section is arranged on the drive disk with the reference plane as the center of symmetry. The reversing section is concave to the first spindle. When the slider is slidably engaged with the reversing section, the intermittent disk moves at the same speed relative to the drive disk. Either the toothed portion or the toothed groove portion is arranged on the second cam portion with the reference plane as the center of symmetry and is located near the position of the turning section closest to the first spindle.

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 slider's cross-section is circular.

5. The transmission device according to claim 1, characterized in that, The number of sliders is N, N≥2n, where 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 toothed portion is disposed on the outer peripheral surface of the intermittent disk and extends radially along the second spindle. The slider is located radially between the toothed portion and the second spindle. There are multiple toothed portions, each corresponding to a slider.

6. The transmission device according to any one of claims 1-5, characterized in that, The drive disk is also provided with a ring body, and the ring body and the first cam part are both located on the outer peripheral side of the second cam part and are arranged at intervals along the circumference of the first spindle; At least one of the ring body and the second cam portion has an arc surface, the arc surface is concentric with the first mandrel, the intermittent disk also has a stationary state, and the slider slides in the stationary state with the arc surface.

7. A laver processing device, characterized in that, include: The machine head claw chain assembly, the curtain frame, and the large box feather chain assembly are provided. The machine head claw chain assembly is used to transport the curtain frame, which is capable of carrying seaweed material. The large box feather chain assembly is connected to the machine head claw chain assembly to transfer the curtain frame. The transmission device is the transmission device according to any one of claims 1-6, wherein the first spindle of the transmission device is connected to the large box feather chain assembly, and the second spindle of the transmission device is connected to the head claw chain assembly. as well as The machine frame, the head claw chain assembly, the large box feather chain assembly and the transmission device are all mounted on the machine frame.

8. The laver processing equipment according to claim 7, characterized in that, The machine head claw chain assembly includes: A first sprocket and a second sprocket, the first sprocket being pivotally connected to the frame, and the second sprocket being sleeved on the second spindle and drivenly connected to the first sprocket via a claw chain; and / or Chain claws are mounted on the claw chain and adapted to engage the curtain frame. There are multiple chain claws arranged at intervals along the conveying direction of the claw chain, and 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. The third sprocket is sleeved on the first spindle, and the fourth sprocket is pivotally mounted on the frame and is connected to the third sprocket via a transition chain. The fourth sprocket is 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, the fifth sprocket being coaxially connected to the fourth sprocket, and the sixth sprocket being pivotally mounted on the frame and driven by the fifth sprocket via a feather chain; and Feather chain rods are mounted on and protrude from the feather chain. There are multiple feather chain rods arranged at intervals along the conveying direction of the feather chain. Any two adjacent feather chain rods and the feather chain together define a receiving groove for accommodating the curtain frame.

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