Driving type anti-blocking device and slide-cut control method

Abstract

This invention discloses a driven anti-clogging device and a sliding cutting control method, comprising: a support mechanism, a transmission mechanism, a first sliding cutting mechanism, a second sliding cutting mechanism, a third sliding cutting mechanism, and a straw-removing mechanism. In the process of agricultural anti-clogging operations, the gearbox is activated, driving the output shaft to rotate. During transmission, due to the change in rotational speed on the first rotating shaft, the first and fourth cutter discs have different speeds than the second and third cutter discs. This allows the driven anti-clogging device to quickly slide-cut the straw using the differential speed cutter discs, resulting in low energy consumption. Furthermore, the device is equipped with a straw-removing mechanism to quickly clean up any remaining straw after cutting, thus improving the overall working efficiency of the driven anti-clogging device.

Description

Technical Field

[0001] This invention relates to the field of agricultural machinery technology, and in particular to a drive-type anti-blocking device and a slip-cutting control method. Background Technology

[0002] Conservation tillage is an agricultural technique that uses techniques such as no-till, reduced-till, and straw mulching to achieve water and moisture conservation, cost reduction, and efficiency improvement. Currently, in the corn-growing areas of Northeast China, when straw is fully returned to the field and stubble is left, the low soil temperature results in poor straw decomposition in the following year. At the same time, the large straw stubble is difficult to cut, which causes serious blockage of no-till planting equipment and affects the operation results.

[0003] Currently, conventional drive-type anti-clogging devices are widely used to cut and clear straw to enable subsequent no-till sowing; however, conventional drive-type anti-clogging devices have high energy consumption, low efficiency, and unsatisfactory cleaning effect. Summary of the Invention

[0004] In view of this, the present invention provides a driven anti-clogging device that uses a differential speed cutter disc to quickly slide and cut straw, resulting in low energy consumption. In addition, the device is equipped with a straw-removing mechanism to quickly clean up the residual straw after cutting, thereby improving the overall working efficiency of the driven anti-clogging device.

[0005] The present invention also provides a sliding shear control method applicable to the above-mentioned drive-type anti-blocking device.

[0006] To achieve the above objectives, the present invention provides the following technical solution:

[0007] As can be seen from the above technical solution, the drive-type anti-clogging device provided by the present invention starts the gearbox during agricultural anti-clogging operations. The gearbox drives the output shaft to rotate. During the transmission process, due to the change in rotation speed on the first rotating shaft, the speeds of the first and fourth cutter discs are different from those of the second and third cutter discs. This allows the drive-type anti-clogging device to quickly cut the straw through the differential cutter discs, resulting in low energy consumption. In addition, the device is also equipped with a straw-removing mechanism to quickly clean up the residual straw after cutting, thus improving the overall working efficiency of the drive-type anti-clogging device.

[0008] This invention also provides a sliding cutting control method, which can be used to design the required segmented sliding cutting disc. Attached Figure Description

[0009] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0010] Figure 1 This is an isometric schematic diagram of the entire drive-type anti-blocking device provided in an embodiment of the present invention;

[0011] Figure 1a This is a top view of the overall drive-type anti-blocking device provided in an embodiment of the present invention;

[0012] Figure 1b This is a front view schematic diagram of the overall drive-type anti-blocking device provided in an embodiment of the present invention;

[0013] Figure 2 This is a schematic diagram of the transmission mechanism of the drive-type anti-blocking device provided in an embodiment of the present invention;

[0014] Figure 3 This is a schematic diagram of the structure of the first sliding cutting mechanism of the drive-type anti-blocking device provided in an embodiment of the present invention;

[0015] Figure 4 This is a schematic diagram of the second sliding cutting mechanism of the drive-type anti-blocking device provided in an embodiment of the present invention;

[0016] Figure 5 This is a schematic diagram of the third sliding cutting mechanism of the drive-type anti-blocking device provided in an embodiment of the present invention;

[0017] Figure 6 This is a schematic diagram of the straw-pulling mechanism of the drive-type anti-blocking device provided in an embodiment of the present invention;

[0018] Figure 7 This is a schematic diagram of the support mechanism of the drive-type anti-blocking device provided in an embodiment of the present invention;

[0019] Figure 8 This is a schematic diagram of the structure of the first cutter head of the first sliding cutting mechanism;

[0020] Figure 9 This is a schematic diagram of the structure of the second cutter head of the second sliding cutting mechanism;

[0021] Figure 10 The flowchart for obtaining the isostatic slip angle curve;

[0022] Figure 11 This is a schematic diagram of differential cutting theory;

[0023] Figure 12A schematic diagram illustrating the derivation of the isostatic slip angle curve;

[0024] Figure 13 A schematic diagram of the statics of straw cutting;

[0025] Figure 14 This is a schematic diagram of the dynamics model when the vehicle has forward velocity.

[0026] Figure 15 This is a grayscale contour plot showing the change in static shear angle at the maximum radius of rotation of the curve under different rotational speeds and forward speeds.

[0027] Figure 16 Gray-scale contour plots of static slip angle changes for a single curve under different rotational speeds and forward speeds;

[0028] Figure 17 This is a schematic diagram of the segmented sliding cutter head curve design based on dynamic sliding angle.

[0029] Among them, 1 is the support mechanism, 101 is the frame, 102 is the grass guard, 103 is the left side plate, 104 is the ground wheel assembly I, 105 is the front side plate I, 106 is the three-point suspension, 107 is the front side plate II, 108 is the front side plate III, 109 is the front side plate IV, 110 is the ground wheel assembly II, 111 is the right side plate, 112 is the towing frame, 113 is the rear side plate I, and 114 is the rear side plate II.

[0030] 2 is the transmission mechanism, 201 is the transmission bearing housing I, 202 is the first rotating shaft, 203 is the second sprocket, 204 is the chain I, 205 is the chain II, 206 is the first sprocket, 207 is the gearbox, 208 is the support plate, 209 is the transmission bearing housing II, and 210 is the first chain;

[0031] 3 is the first sliding cutting mechanism, 301 is the double-row small sprocket II, 302 is the chain III, 303 is the chain IV, 304 is the flange I, 305 is the second rotating shaft, 306 is the vertical bearing seat I, 307 is the double-row large sprocket II 307, 308 is the pin I, 309 is the first cutter head, and 310 is the second chain;

[0032] 4 is the second sliding cutting mechanism, 401 is the double-row small sprocket III, 402 is the chain V, 403 is the chain VI, 404 is the second cutter head, 405 is the pin II, 406 is the third rotating shaft, 407 is the vertical bearing seat III 407, 408 is the vertical bearing seat IV, 409 is the double-row large sprocket, 410 is the pin III, 411 is the third cutter head, and 412 is the third chain;

[0033] 5 is the third sliding cutting mechanism, 501 is the fourth cutter head, 502 is the pin IV, 503 is the fourth rotating shaft, 504 is the chain VII, 505 is the chain VIII, 506 is the double-row large sprocket IV, 507 is the vertical bearing seat V, 508 is the flange II, 509 is the double-row small sprocket IV, and 510 is the fourth chain;

[0034] 6 is the straw-picking mechanism, 601 is the straw-picking wheel I, 602 is the pin V, 603 is the vertical bearing seat, 604 is the fifth rotating shaft, 605 is the vertical bearing seat, 606 is the double-row large sprocket V, 607 is the pin VI, 608 is the straw-picking wheel II, 609 is the chain IX, 610 is the chain X, 611 is the double-row small sprocket, and 612 is the fifth chain. Detailed Implementation

[0035] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0036] The drive-type anti-blocking device provided in this embodiment of the invention includes: a support mechanism 1, a transmission mechanism 2, a first sliding cutting mechanism 3, a second sliding cutting mechanism 4, a third sliding cutting mechanism 5, and a straw-pulling mechanism 6, as shown. Figures 1-9 As shown;

[0037] The transmission mechanism 2 includes: a gearbox 207, a first chain 210, an output shaft 211, and a first rotating shaft 202 for changing the rotation speed;

[0038] The first sliding cutting mechanism 3 includes: a second chain 310, a second rotating shaft 305, and a first cutter disc 309 for sliding cutting straw;

[0039] The second sliding cutting mechanism 4 includes: a third chain 412, a third rotating shaft 406, and a second cutter disc 404 and a third cutter disc 411, both used for sliding cutting straw.

[0040] The output shaft 211 passes through the gearbox 207. The first end of the output shaft 211 is connected to the first rotating shaft 202 via the first chain 210. The second rotating shaft 305 is connected to the first rotating shaft 202 via the second chain 310. The first cutter head 309 is concentrically mounted on the first end of the second rotating shaft 305 to obtain the first rotational speed.

[0041] The fourth rotating shaft 503 is connected to the first rotating shaft 202 via the fourth chain 510; the fourth cutter head 501 is concentrically mounted on the first end of the fourth rotating shaft 503 to obtain the first rotational speed.

[0042] The second end of the output shaft 211 is connected to the third rotating shaft 406 via the third chain 412. The second cutter head and the third cutter head are respectively concentrically mounted at both ends of the third rotating shaft 406 to obtain the second rotation speed.

[0043] The first cutter head 309 and the second cutter head 404 are arranged at intervals relative to each other, and the third cutter head 411 and the fourth cutter head 501 are arranged at intervals relative to each other.

[0044] The first speed and the second speed are different;

[0045] The second end of the second rotating shaft 305 and the second end of the fourth rotating shaft 503 can be rotatably mounted on the support mechanism 1; the first rotating shaft 202 and the third rotating shaft 406 can be rotatably mounted on the support mechanism 1; the straw-pulling mechanism 6 is mounted on the support mechanism 1.

[0046] In the above scheme, the first rotating shaft 202 enables the first cutter disc 309 and the fourth cutter disc 501 to obtain a first rotational speed, while the second cutter disc 404 and the third cutter disc 411 obtain a second rotational speed. The basic principle is that during agricultural anti-clogging operations, the gearbox 207 is started, which drives the output shaft 211 to rotate. During the transmission process, due to the change in rotational speed on the first rotating shaft 202, the speeds of the first cutter disc 309 and the fourth cutter disc 501 are different from those of the second cutter disc 404 and the third cutter disc 411. This allows the drive-type anti-clogging device to quickly cut the straw through the differential cutter discs, resulting in low energy consumption. In addition, the device is also equipped with a straw-removing mechanism 6 to quickly clean up the residue after cutting.

[0047] Furthermore, the speed of the first rotational speed is lower than that of the second rotational speed, and the rotation direction of both the first and second rotational speeds is clockwise (forward rotation).

[0048] In this scheme, the first cutter head 309 and the fourth cutter head 501 slide cut the straw at the same low speed, while the second cutter head 404 and the third cutter head 411 slide cut the straw at the same high speed. By simultaneously using high-speed and low-speed sliding cuts, the energy consumption of the operation is further reduced while ensuring the cutting effect.

[0049] In this plan, such as Figure 2 As shown, a first sprocket 206 is fitted onto the first end of the output shaft 211;

[0050] A second sprocket 203 is mounted on the first rotating shaft 202. The radius of the second sprocket 203 is different from that of the first sprocket 206. The first sprocket 206 is connected to the second sprocket 203 by a first chain 210.

[0051] This configuration causes the rotational speed of the output shaft 211 to change when it is transmitted to the first rotating shaft 202 via the first chain 210, thereby giving the cutter head different rotational speeds.

[0052] Preferably, the first sprocket 206 is a double-row small sprocket I, and the second sprocket 203 is a double-row large sprocket I; the radius of the double-row small sprocket I is larger than the radius of the double-row large sprocket I. This arrangement ensures that the speed of the first rotational speed is lower than the speed of the second rotational speed.

[0053] As a preferred option, such as Figures 2-7 As shown, a double-row small sprocket Ⅲ401 is fitted on the second end of the output shaft 211; a double-row small sprocket Ⅱ301 and a double-row small sprocket Ⅳ509 are also fitted on the first rotating shaft 202 in sequence; a double-row large sprocket Ⅱ307 is fitted on the second rotating shaft 305; a double-row large sprocket Ⅲ409 is fitted on the third rotating shaft 406; and a double-row large sprocket Ⅳ506 is fitted on the fourth rotating shaft 503.

[0054] Among them, the radii of double-row small sprockets I, II 301, III 401, and IV 509 are all equal, and the radius of double-row large sprocket I is greater than that of double-row small sprockets I; the radii of double-row large sprockets II 307, III 409, and IV 506 are all equal, and their radii are less than or equal to the radius of double-row large sprocket I (i.e., the second sprocket 203) and greater than the radius of double-row small sprocket I (i.e., the first sprocket 206);

[0055] Double-row small sprocket II 301 is connected to double-row large sprocket II 307 via a second chain 310; double-row small sprocket IV 509 is connected to double-row small sprocket IV 509 via a fourth chain 510; double-row small sprocket III 401 is connected to double-row large sprocket III 409 via a third chain 412.

[0056] Furthermore, a double-row small sprocket Ⅲ401 is fitted on the second end of the output shaft 211, and the radius of the double-row small sprocket Ⅲ401 is the same as the radius of the double-row small sprocket Ⅱ301; a double-row large sprocket Ⅲ409 is fitted on the third chain 310, and the radius of the double-row large sprocket Ⅲ409 is the same as the radius of the double-row large sprocket Ⅱ307; wherein, the double-row small sprocket Ⅲ401 is connected to the double-row large sprocket Ⅲ409 through the third chain 412.

[0057] With the above settings, the second rotational speed obtained by the second cutter head 404 and the third cutter head 411 is height, and the first rotational speed obtained by the first cutter head 309 and the fourth cutter head 501 is speed.

[0058] It should be noted that the first chain 210, the second chain 310, the third chain 412, and the fourth chain 510 are all double chains. The first chain 210 includes chain I 204 and chain II 205; the second chain 310 includes chain III 302 and chain IV 303; the third chain 412 includes chain V 402 and chain VI 403; and the fourth chain 510 includes chain VII 504 and chain VIII 505.

[0059] In this plan, such as Figure 1 As shown, the second rotating shaft 305, the third rotating shaft 406, and the fourth rotating shaft 503 are arranged horizontally and coaxially at intervals.

[0060] The first cutter head 309, the second cutter head 404, the third cutter head 411, and the fourth cutter head 501 all have the same radius.

[0061] The above settings allow for better coordination between the blades, greatly improving the efficiency of straw cutting.

[0062] In this design, the straw-picking mechanism 6 includes: a fifth chain 612, a fifth rotating shaft 604, and two straw-picking wheels;

[0063] The fifth rotating shaft 604 is connected to the first rotating shaft 202 via the fifth chain 612, and the two straw-picking wheels are concentrically installed at both ends of the fifth rotating shaft 604;

[0064] The fifth rotating shaft 604 is installed at the lower part of the support mechanism 1. In this scheme, two straw-pulling wheels are used to quickly clean up the residual straw after cutting.

[0065] In this plan, such as Figures 8-9 As shown, the first cutter head 309, the second cutter head 404, the third cutter head 411, and the fourth cutter head 501 are called cutter heads;

[0066] The cutter head includes: a cutter head body and a plurality of sliding cutting blades evenly arranged along the outer periphery of the cutter head, each sliding cutting blade having a plurality of equal and sequentially connected sliding cutting teeth.

[0067] The above settings further improve the speed of straw cutting.

[0068] In this scheme, the static sliding angles of the first cutter head 309 and the fourth cutter head 501 are the same;

[0069] The static sliding angles of the second cutter head 404 and the third cutter head 411 are the same;

[0070] The static sliding angles of the first cutter head 309 and the fourth cutter head 501 are greater than those of the second cutter head 404 and the third cutter head 411.

[0071] The above settings reduce power consumption during straw cutting operations and effectively prevent straw movement that could cause blockages.

[0072] In this design, the dynamic sliding angle of the second cutter head 404 and the third cutter head 411 is 37.5°. This setting achieves better cutting results while reducing cutting power consumption.

[0073] The present invention also discloses a sliding control method applicable to the above-mentioned drive-type anti-blocking device, the method being as follows:

[0074] Based on pre-set parameters, the drive-type anti-blocking device performs sliding cutting motion along each segment of the pre-divided isostatic sliding cutting angle curve, and performs double forward differential sliding cutting on the target object.

[0075] Among them, the pre-set parameters include at least the stable range value of the static shear angle in each segment of the static shear angle curve;

[0076] The sliding cutting motion includes: the gearbox 207 of the drive anti-blocking device is started, and the first shaft 202 is driven to rotate through the first end of the output shaft 211 of the gearbox 207; then the first shaft 202 drives the first cutter head 309 mounted on the second shaft 305 to rotate at a first speed, and at the same time drives the fourth cutter head 501 mounted on the fourth shaft 503 to rotate at the first speed; the second end of the output shaft 211 drives the second cutter head 404 and the third cutter head 411 mounted on the third shaft 406 to rotate at a second speed;

[0077] The process of obtaining the pre-set isostatic sliding angle curve involved in the sliding control of the aforementioned drive-type anti-clogging device includes:

[0078] M111: Based on the parameters of the sliding cutter head, construct an isostatic sliding angle function model for the sliding cutter head;

[0079] M112: Input the sliding cutter head parameters into the static sliding angle function model to obtain the static sliding angle of the corresponding sliding cutter head;

[0080] like Figure 10 A dual-forward rotation drive anti-blocking method based on sliding shear is shown in the figure. The design process of the dual-forward rotation drive anti-blocking method can be derived according to the steps specified therein.

[0081] like Figure 11 A theoretical model for dual-rotation differential cutting was constructed. Under the differential cutting of the two blades, the straw increases the normal stress per unit area through stress superposition, thereby achieving a better cutting effect.

[0082] like Figure 12A static sliding angle function model for cutter head cutting is constructed, and the curve equation is derived.

[0083] like Figure 10 As shown, a static sliding angle function model for cutter head cutting is constructed and the curve equation is derived:

[0084]

[0085] The above is Formula 1, where r is the radius of gyration at point A. Let C be the radius of rotation. Let be the angle between points A and C.

[0086] M113: Determine the parameters of the static shear angle curve based on the static shear angle, and construct the static shear angle curve;

[0087] Integrating Equation 1, we get: Formula 2, where c is a constant. It is an isostatic sliding angle.

[0088] Formula 2 is the equation of the static shear angle curve, from which the static shear angle curve is derived.

[0089] The process of obtaining the stable interval value of the equal slip angle in each segment of the isostatic slip angle curve includes:

[0090] like Figure 13 S111: Based on static analysis, a static model of the slip curve is constructed using the force parameters obtained from the force analysis during the slip cutting of the sample, which is straw.

[0091] A static model of the cutting curve is constructed based on static analysis, such as... Figure 13 As shown, based on the forces acting on the straw, to prevent the straw from moving laterally, we can solve the following equations simultaneously:

[0092]

[0093] Formula 3

[0094] α is the angle between the cutting point and the vertical direction of the ground, F1 is the normal force exerted by the cutter head on the straw, F f1 F is the frictional force between the cutter head and the straw, and F is the supporting force of the ground on the straw. f μ1 is the frictional force between the ground and the straw, μ2 is the frictional coefficient between the cutter head and the straw, and F2 is the normal stress of the notched cutter head on the straw.

[0095] At this time, the normal pressure F1 exerted by the cutter head on the straw can be expressed as:

[0096] Formula 4

[0097] Combining formulas 3 and 4, we get:

[0098] Formula 5

[0099] Transforming Equation 5, we get:

[0100] Formula 6

[0101] S112: Input the sample parameters, sliding cutter head parameters, and operating parameters into the static model to obtain the parameter range of the isostatic sliding angle curve;

[0102] h is the depth of burial, r A Let d be the radius of gyration at point A, d be the diameter of the corn stalk, and r be the maximum radius of gyration. Using Formula 6, the soil penetration depth, maximum radius of gyration, minimum radius of gyration, the friction angle between the stalk and the cutter head, and the friction angle between the stalk and the soil are determined to define the range of the slip angle. In this case, the maximum radius of gyration is 215mm, the minimum radius of gyration is 150mm, the soil penetration depth is 70mm, the friction angle between the stalk and the cutter head is 20°, and the friction angle between the stalk and the ground is 30°. Therefore, α ranges from 34.24° to 55.75°. According to Formula 6, the static slip angle τ ≥ 45.76°.

[0103] S113: Based on the parameter range of the isostatic shear angle curve and the forward sample velocity, construct the first function model of the isostatic shear angle variation with rotational speed and forward velocity on the isostatic shear angle curve;

[0104] Establish a functional model of the slip angle on the isostatic slip angle curve with respect to rotational speed and forward speed, as follows: Figure 14 As shown, the contact point slip angle on the curve can be expressed as:

[0105] The above is Formula 7, where v is the horizontal speed (i.e., the horizontal operating speed of this drive-type anti-blocking device). Let n be the dynamic sliding angle at point A, and n be the rotational speed of the cutter head.

[0106] like Figure 14 The operation parameters are input into the first function model to obtain the dynamic sliding angles on each static sliding angle curve;

[0107] S114: Based on the dynamic sliding angle, the changed rotational speed and the forward speed on each constant static sliding angle curve, the constant static sliding angle on each constant static sliding angle curve is obtained using the first function model;

[0108] S115: Select multiple isostatic shear angle curves, perform shearing and connect them to form a segmented shear angle curve. Collect the isostatic shear angles of each isostatic shear angle curve in the segmented shear angle curve to obtain the stable interval value of the isostatic shear angle of each segmented isostatic shear angle curve.

[0109] Furthermore, after constructing a first function model of the static slip angle variation with rotational speed and forward speed based on the parameter range of the static slip angle curve and the forward sample speed, the model also includes:

[0110] Based on the formulas for the variation of dynamic shear angle and static shear angle at the maximum radius of gyration, the variation law of static shear angle at the maximum radius of gyration is obtained.

[0111] Analyzing the dynamic variation law of the slip angle at the maximum radius of gyration, and substituting the previously determined parameters, the formula for the change in the slip angle at the maximum radius of gyration is obtained as follows:

[0112]

[0113] The above is Formula 8, which analyzes the maximum change of the static shear angle on the same static shear angle curve at the same rotational speed and forward speed, based on the variation law of the static shear angle at the maximum turning radius.

[0114] Now import Formula 8 into Origin to generate... Figure 15 The variation law of the sliding angle at the maximum radius of gyration can be analyzed from the figure;

[0115] like Figure 16 The maximum change in the slip angle on the same curve is analyzed under the same rotational speed and forward speed, which can be represented by Formula 9.

[0116]

[0117] In the formula r represents the maximum change in the shear angle on the same curve. max and r min These are the maximum and minimum slewing radii, respectively.

[0118] At this point, the maximum variation law of the shear angle on the same curve can be derived from... Figure 15 express;

[0119] like Figure 17 By using the dynamic sliding angle after the same rotation speed and the change of forward speed, the static sliding angle of the curve is deduced. Multiple curves with equal static sliding angles are selected to process the cutting curve in segments, ensuring that the sliding angle in each segment of the curve is in a stable range.

[0120] The working process of this invention:

[0121] The power output shaft of the tractor drives the gearbox 207. The second end of the output shaft 211 of the gearbox drives the second sliding cutting mechanism 4 to perform high-speed rotation in the seed row via chain drive. The first end of the gearbox 207 drives the first rotating shaft 202 via chain drive. The left and right sides of the first rotating shaft 202 drive the first sliding cutting mechanism 3 and the third sliding cutting mechanism 5 to perform low-speed rotation respectively via chain drive. At the same time, the output shaft 211 drives the straw-picking mechanism 6 via chain drive to clean up the stubble and straw in the seed row after the cutting operation.

[0122] The technical features mentioned above, those to be mentioned below, and those shown individually in the accompanying drawings can be combined arbitrarily, provided that the combined technical features are not contradictory. All feasible combinations of features are the technical content explicitly described herein. Any one of the multiple sub-features contained in the same statement can be applied independently, without necessarily being applied together with other sub-features.

[0123] The present invention also provides examples, and therefore has corresponding beneficial effects, which can be referred to in the foregoing description, and will not be repeated here.

[0124] The following is a further description of this solution with reference to specific embodiments:

[0125] Support mechanism 1 (i.e., support connection mechanism) includes frame 101, grass baffle 102, left side plate 103, ground wheel assembly I 104, front side plate I 105, three-point suspension 106, front side plate II 107, front side plate III 108, front side plate IV 109, ground wheel assembly II 110, right side plate 111, traction frame 112, rear side plate I 113, and rear side plate II 114; support mechanism 1 is located above and fixed to the first sliding cutting mechanism 3, the second sliding cutting mechanism 4, the third sliding cutting mechanism 5, and the straw pulling mechanism 6, and is also located below and fixed to the transmission mechanism 2; left side plate 103, right side plate 111 The ground wheel assembly I 104 and ground wheel assembly II 110 are fixed to both sides of the frame 101 by welding. They are connected to the left side plate 103 and the right side plate 111 by thread. The front side plate I 105, front side plate II 107, front side plate III 108, front side plate IV 109, rear side plate I 113 and rear side plate II 114 are fixed to the bottom of the frame 101 by welding, which serves to support and connect the drive mechanism. The three-point suspension 106 is fixed to the front of the frame 101 by welding. The grass baffle 102 and the traction frame 112 are fixed to the rear of the frame by welding. The grass baffle 102 prevents the stubble and straw from flying after operation.

[0126] Preferably, the transmission mechanism 2 is placed above the frame 101 by setting a support beam, thereby preventing the movement of straw and stubble and thus affecting its operation; the grass baffle 102 is 200mm above the ground, which can effectively prevent the stubble and straw generated after the straw pulling mechanism 6 operates; the upper suspension of the three-point suspension 106 is designed with support beams on both sides, thereby improving the connection strength of the three-point suspension mechanism and enhancing the connection stability.

[0127] The transmission mechanism 2 (i.e., the intermediate transmission mechanism) includes a transmission bearing housing I 201, a first rotating shaft 202, a double-row large sprocket I (i.e., the second sprocket 203), a chain I 204, a chain II 205, a double-row small sprocket (i.e., the first sprocket 206), a gearbox 207, a support plate 208, and a transmission bearing housing II 209. The transmission bearing housing I 201, the support plate 208, and the transmission bearing housing II 209 are fixed to the frame 101 by threaded connection. The second sprocket 203 is fixed to the first rotating shaft 202 by threaded connection. The first sprocket 206 is positioned by a shaft shoulder and a threaded connection and is driven by a flat key. The gearbox 207 is fixed above the support plate 208 by welding.

[0128] Preferably, the support plate 208 is fixed to the frame 101 by threads and fixed to the gearbox 207 by welding, which can significantly improve the support stability and make the machine maintain smooth transmission when operating in the field.

[0129] The first sliding cutting mechanism 3 (i.e., the first low-speed forward sliding cutting mechanism) includes a double-row small sprocket II 301, chain III 302, chain IV 303, flange I 304, a second rotating shaft 305 (i.e., the low-speed rotating shaft), a vertical bearing seat I 306, a double-row large sprocket II 307, a pin I 308, and a first cutter head 309 (i.e., the low-speed segmented sliding cutting cutter head I). The double-row small sprocket II 301 is fixed to the first rotating shaft 202 by a threaded connection, and the flange I 304 and the vertical bearing seat I 306 are respectively fixed to the left side by threads. Plate 103, front side plate I 105, and double-row small sprockets 307 are fixed to the second rotating shaft 305 by threaded connection. The first cutter head 309 is fixed to the second rotating shaft 305 by pin I 308. The first cutter head 309 and the second cutter head 104 (i.e., the high-speed segmented sliding cutter head I) perform cutting operations on the same side. The first cutter head 309 and the second cutter head 104 (which plays a differential cutting role during high-speed cutting and improves the cutting effect through stress superposition effect and support cutting effect) and reduce the power consumption of operation by generating a sliding cutting effect through the low speed equal sliding angle curve.

[0130] Preferably, the first cutter head 309 is powered by chain drive for field operations. The blade curve of the cutter head is derived by dynamic analysis and calculation. At the same time, the segmented design ensures that each segment of the cutting curve is in a large and stable sliding angle range, so that the straw does not move during the cutting process and the cutting power consumption is low. The first cutter head 309 performs cutting operations on the same side as the second cutter head 404. When cutting at high speed with the second cutter head 40, it plays a differential cutting role and improves the row operation effect through stress superposition effect and support cutting effect. At the same time, the sliding cutting effect generated by the low speed constant sliding angle curve reduces the operation power consumption.

[0131] The second sliding cutting mechanism 4 (i.e., the high-speed forward sliding cutting mechanism) includes a double-row small sprocket Ⅲ401, chain Ⅴ402, chain Ⅵ403, a second cutter head 404, pin Ⅱ405, a third rotating shaft 406 (i.e., the high-speed shaft), a vertical bearing seat Ⅲ407, a vertical bearing seat Ⅳ408, a double-row large sprocket Ⅲ409, pin Ⅲ410, and a third cutter head 411 (i.e., the high-speed segmented sliding cutting cutter head Ⅱ). The double-row small sprocket Ⅲ401 is fixed by threaded connection and shaft shoulder, and is driven by a flat key. The vertical bearing seat Ⅲ407, vertical... Bearing seat Ⅳ408 is fixed to front side plate Ⅱ107 and front side plate Ⅲ108 by threads. Double row large sprocket Ⅲ409 is positioned by threaded connection. Second cutter head 404 and third cutter head 411 are fixed to third rotating shaft 406 by pin shaft Ⅱ405 and pin shaft Ⅲ410. Second cutter head 404, third cutter head 411, first cutter head 309 and fourth cutter head 501 simultaneously perform differential cutting on the root stubble in the planting row and the straw covering the ground. At the same time, the high speed iso-slip angle curve ensures the cutting effect while reducing the power consumption of operation.

[0132] The third sliding cutting mechanism 5 (i.e., the second low-speed forward sliding cutting mechanism) includes a fourth cutter head 501 (i.e., low-speed segmented sliding cutting cutter head II), a pin shaft IV 502, a fourth rotating shaft 503 (i.e., low-speed shaft II), a chain VII 504, a chain VIII 505, a double-row large sprocket IV 506, a vertical bearing seat V 507, a flange II 508, and a double-row small sprocket IV 509; the double-row large sprocket IV 506 is fixed to the first rotating shaft 202 by a threaded connection, and the flange II 508 and the vertical bearing seat V 507 are respectively fixed by threads. The right side plate 111 and the front side plate Ⅳ109 are fixed together. The double-row small sprockets Ⅳ509 are fixed to the fourth rotating shaft 503 by threaded connection. The low-speed segmented sliding cutting disc Ⅱ501 is fixed to the fourth rotating shaft 503 by the pin Ⅳ502. The fourth cutting disc 501 and the third cutting disc 411 perform cutting operations on one side at the same time. When cutting at high speed with the third cutting disc 411, it plays a differential cutting role and improves the cutting effect through stress superposition effect and support cutting effect. At the same time, the sliding cutting effect is generated by the low speed equal sliding angle curve to reduce the power consumption of operation.

[0133] Preferably, the fourth cutter head 501 is powered by chain drive for field operations. The blade curve of the cutter head is derived by dynamic analysis and calculation. At the same time, the segmented design ensures that each segment of the cutting curve is in a large and stable sliding angle range, so that the straw does not move during the cutting process and the cutting power consumption is low. The fourth cutter head 501 performs cutting operations on one side of the third cutter head 411. When the third cutter head 411 cuts at high speed, it plays a differential cutting role and improves the row operation effect through stress superposition effect and support cutting effect. At the same time, the sliding cutting effect generated by the low speed constant sliding angle curve reduces the operation power consumption.

[0134] The straw-picking mechanism 6 (i.e., the low-speed forward-rotating straw-picking mechanism) includes a straw-picking wheel I 601, a pin V 602, a vertical bearing seat VI 603, a fifth rotating shaft 604 (i.e., the rear axle), a vertical bearing seat VII 605, a double-row large sprocket V 606, a pin VI 607, a straw-picking wheel II 608, a chain IX 609, a chain X 610, and a double-row small sprocket V 611; the double-row small sprocket V 611 is fixed to the first [unclear - possibly a specific component or part] by a threaded connection. The rotating shaft 202 and the double-row large sprocket V606 are fixed to the rear shaft 604 by threaded connection. The vertical bearing seats VI603 and VII605 are fixed to the rear side plates I113 and II114 by threaded connection. The straw-pulling wheels I601 and II608 are fixed to the rear shaft 604 by pins V602 and VI607. The straw-pulling wheels clean up the stubble and straw residue left after cutting.

[0135] Preferably, the straw-pulling wheel I 601 and the straw-pulling wheel II 608 are powered by chain drive to clear away the straw and stubble cut in the seed row, thereby reducing the blockage rate of the seeder during sowing and improving the throughput of the seeder.

[0136] In some embodiments, the first cutter head 309, the second cutter head 404, the third cutter head 411, and the fourth cutter head 501 respectively perform differential speed cutting operations on the surface straw. The first cutter head 309 and the fourth cutter head 501 play a supporting role in the cutting process, and at the same time, by changing the arrangement distance of the cutter heads, they generate a stress superposition effect on the straw, thereby improving the cutting effect.

[0137] In some embodiments, after the first sliding cutting mechanism 3, the second sliding cutting mechanism 4, and the third sliding cutting mechanism 5 perform differential cutting of straw and stubble, the straw-pulling mechanism 6 cleans up the remaining cut material by power drive. By changing the operation sequence of cutting first and then pulling, the original anti-blocking device is unable to handle the stubble by pulling first and then cutting. At the same time, the driven straw-pulling mechanism has a higher cleaning effect than the original passive straw-pulling mechanism.

[0138] In some embodiments, such as Figure 8The first cutter head, 309, uses a static constant sliding angle curve for its blade edge. Dynamic analysis is used to derive the curve's geometric parameters, ensuring that the straw does not shift during cutting while maintaining low cutting power consumption. The three curve segments are as follows: The polar coordinate equation, The unit of angle is rad, and r is the unit of distance from the center of the circle is mm. Simultaneously, the first cutter head 309, relative to the second cutter head 404, provides support and stress superposition during the cutting process. The two rotate at different speeds. The first cutter head 309 operates at a speed of 190 revolutions per minute, with a maximum rotation radius of 215 mm and a soil penetration depth of 70 mm.

[0139] In some embodiments, such as Figure 9 The second cutter head is made of 404 stainless steel. The cutting edge curve uses a static constant sliding angle curve. Through bench tests and simulation data, dynamic analysis and segmented design were employed to ensure that the cutting edge curve maintains cutting effectiveness while achieving low cutting power consumption during the cutting process. The three curve segments are as follows: , , The polar coordinate equation, The unit of angle is rad, and r is the unit of distance from the center of the circle is mm. Simultaneously, this cutter head and the first cutter head 309 perform differential cutting. While the first cutter head 309 is in contact with the straw, this cutter head quickly completes the cutting operation. The second cutter head 404 operates at a speed of 360 r / min, has a maximum rotation radius of 215 mm, and a soil penetration depth of 70 mm, enabling it to completely cut the stubble.

[0140] In some embodiments, the blade curves of the first cutter head 309 and the fourth cutter head 501 are selected as equal sliding angle curves with a larger static equal sliding angle. At the same time, the segmented structural design ensures that the sliding angle remains stable in the optimal range during operation, which can effectively prevent straw movement and blockage while reducing power consumption.

[0141] In some embodiments, the blade curves of the second cutter head 404 and the third cutter head 411 are selected as static equal sliding angle curves. A segmented design is adopted for each segment of the curve so that the dynamic sliding angle is in the optimal range of 37.5° for corn stalk cutting during operation, thereby reducing cutting power consumption while achieving good cutting results.

[0142] In some embodiments, a power-type differential cutting-splitting integrated operation combination is defined. After the first sliding cutting mechanism 3, the second sliding cutting mechanism 4 and the third sliding cutting mechanism 5 perform double forward differential cutting, the straw-splitting mechanism 6 cleans up the residue after cutting.

[0143] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on the differences from other embodiments. The same or similar parts between the various embodiments can be referred to each other.

[0144] The above description of the disclosed embodiments enables those skilled in the art to make or use the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A drive-type anti-blocking device, characterized in that, include: Support mechanism (1), transmission mechanism (2), first sliding cutting mechanism (3), second sliding cutting mechanism (4), third sliding cutting mechanism (5) and straw pulling mechanism (6); The transmission mechanism (2) includes: a gearbox (207), a first chain (210), an output shaft (211), and a first rotating shaft (202) for changing the rotation speed. The first sliding cutting mechanism (3) includes: a second chain (310), a second rotating shaft (305), and a first cutter disc (309) for sliding cutting straw. The second sliding cutting mechanism (4) includes: a third chain (412), a third rotating shaft (406), and a second cutter disc (404) and a third cutter disc (411), both used for sliding cutting straw. The third sliding cutting mechanism (5) includes: a fourth chain (510), a fourth rotating shaft (503), and a fourth cutter disc (501) for sliding cutting straw. The output shaft (211) passes through the gearbox (207). The first end of the output shaft (211) is connected to the first rotating shaft (202) via the first chain (210). The second rotating shaft (305) is connected to the first rotating shaft (202) via the second chain (310). The first cutter head (309) is concentrically mounted on the first end of the second rotating shaft (305) to obtain a first rotational speed. The fourth rotating shaft (503) is connected to the first rotating shaft (202) via the fourth chain (510); the fourth cutter head (501) is concentrically mounted on the first end of the fourth rotating shaft (503) to obtain a first rotational speed; The second end of the output shaft (211) is connected to the third rotating shaft (406) via the third chain (412). The second cutter head (404) and the third cutter head (411) are respectively concentrically mounted at both ends of the third rotating shaft (406) to obtain a second rotation speed. The first cutter head (309) and the second cutter head (404) are arranged at a distance from each other, and the third cutter head (411) and the fourth cutter head (501) are arranged at a distance from each other. The first rotational speed and the second rotational speed are different; The second end of the second rotating shaft (305) and the second end of the fourth rotating shaft (503) can be rotatably mounted on the support mechanism (1); the first rotating shaft (202) and the third rotating shaft (406) can be rotatably mounted on the support mechanism (1); the straw-pulling mechanism (6) is mounted on the support mechanism (1). The first cutter head (309) and the fourth cutter head (501) have the same static sliding angle; The second cutter head (404) and the third cutter head (411) have the same static sliding angle; The static sliding angles of the first cutter head (309) and the fourth cutter head (501) are greater than the static sliding angles of the second cutter head (404) and the third cutter head (411).

2. The drive-type anti-blocking device according to claim 1, characterized in that, The speed of the first rotational speed is lower than that of the second rotational speed, and the rotation directions of the first rotational speed and the second rotational speed are both clockwise.

3. The drive-type anti-blocking device according to claim 1, characterized in that, The first end of the output shaft (211) is fitted with a first sprocket (206). A second sprocket (203) is fitted onto the first rotating shaft (202), and the radius of the second sprocket (203) is different from the radius of the first sprocket (206). The first sprocket (206) is connected to the second sprocket (203) via the first chain (210).

4. The drive-type anti-blocking device according to claim 1, characterized in that, The second rotating shaft (305), the third rotating shaft (406), and the fourth rotating shaft (503) are arranged horizontally and coaxially at intervals; The first cutter head (309), the second cutter head (404), the third cutter head (411), and the fourth cutter head (501) all have the same radius.

5. The drive-type anti-blocking device according to claim 1, characterized in that, The straw-picking mechanism (6) includes: a fifth chain (612), a fifth rotating shaft (604), and two straw-picking wheels; The fifth rotating shaft (604) is connected to the first rotating shaft (202) via the fifth chain (612), and the two straw-picking wheels are concentrically installed at both ends of the fifth rotating shaft (604); The fifth rotating shaft (604) is installed at the lower part of the support mechanism (1).

6. The drive-type anti-blocking device according to claim 1, characterized in that, The first cutter head (309), the second cutter head (404), the third cutter head (411), and the fourth cutter head (501) are referred to as cutter heads; The cutter head includes: a cutter head body and a plurality of sliding cutting blades evenly arranged along the outer periphery of the cutter head, each of the sliding cutting blades having a plurality of equal and sequentially connected sliding cutting teeth.

7. The drive-type anti-blocking device according to claim 1, characterized in that, The dynamic sliding angle of the second cutter head (404) and the third cutter head (411) is 37.5°.

8. A sliding shear control method, characterized in that, Applicable to the drive-type anti-clogging device as described in any one of claims 2-7; Based on pre-set parameters, the drive-type anti-blocking device is driven to perform sliding cutting motion along each segment of the pre-divided static sliding cutting angle curve, and performs double positive rotation differential sliding cutting on the target object; Among them, the pre-set parameters include at least the stable range value of the static shear angle in each segment of the static shear angle curve; The sliding cutting motion includes: the gearbox (207) of the drive anti-blocking device is started, and the first shaft (202) is driven to rotate through the first end of the output shaft (211) of the gearbox (207); then the first shaft (202) drives the first cutter disc (309) set on the second shaft (305) to rotate at a first speed, and at the same time drives the fourth cutter disc (501) set on the fourth shaft (503) to rotate at a first speed; the second end of the output shaft (211) drives the second cutter disc (404) and the third cutter disc (411) set on the third shaft (406) to rotate at a second speed; The process of obtaining the pre-set isostatic shear angle curve includes: Based on the parameters of the sliding cutter head, an isostatic sliding angle function model is constructed for the sliding cutter head. The static sliding angle of the corresponding sliding cutter head is obtained by inputting the sliding cutter head parameters into the static sliding angle function model. The parameters of the static shear angle curve are determined based on the static shear angle, and the static shear angle curve is constructed. The process of obtaining the stable interval value of the static shear angle in each segment of the static shear angle curve includes: Based on static analysis, a static model of the slip curve is constructed using the force parameters obtained from the force analysis during the slip shearing of the sample. Input the sample parameters, sliding cutter head parameters, and operating parameters into the static model to obtain the parameter range of the isostatic sliding angle curve; Based on the parameter range of the isostatic shear angle curve and the forward sample velocity, a first function model is constructed to show how the isostatic shear angle on the isostatic shear angle curve changes with the rotational speed and the forward velocity. The operation parameters are input into the first function model to obtain the dynamic sliding angles on each static sliding angle curve. Based on the dynamic sliding angle, the changed rotational speed, and the forward speed on each constant static sliding angle curve, the constant static sliding angle on each constant static sliding angle curve is obtained using the first function model; Multiple isostatic shear angle curves are selected, sheared, and connected to form a segmented shear curve. The isostatic shear angles of each isostatic shear angle curve in the segmented shear curve are collected to obtain the stable interval value of the isostatic shear angle of each segment of the isostatic shear angle curve.

9. The sliding shear control method according to claim 8, characterized in that; After constructing the first function model of the static slip angle variation with rotational speed and forward speed on the static slip angle curve based on the parameter range and forward sample speed of the static slip angle curve, the model further includes: Based on the formulas for the variation of the dynamic shear angle and the static shear angle at the maximum radius of gyration, the variation law of the static shear angle at the maximum radius of gyration is obtained. Based on the analysis of the variation law of the static shear angle at the maximum turning radius, the maximum change of the static shear angle on the same static shear angle curve is analyzed at the same rotational speed and forward speed.

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