Development of a strip fertilization planter for rice straw crushing with back-throwing and interrow-laying

Background: In order to improve the current situations in rice-wheat rotation region in the middle and lower reaches of the Yangtze River, such as large amount of rice straw, complex returning process, short-time stubble connection, high power consumption, poor smoothness and especially unstable performance, and further promote the resource utilization process of full straw returning in Jiangsu province, this study combined with the agronomic requirements of wheat sowing in rice-stubble land, a strip fertilization planter for straw crushing with back-throwing and interrow-laying in full stubble elds was developed. Results: Structural design and theoretical analysis were carried out on key components such as straw crushing device, broken-straw control device, soil rotary-tillage device and power transmission device, etc., to determine the corresponding structure and operating performance parameters, and then the eld performance and verication tests were completed on the uniformity of inter-row mulching-straw Y 1 and the variability of seed-band width Y 2 . The results showed that the crushing spindle rotation-speed A had an extremely signicant impact on Y 1 , followed by the machine ground speed B. The conveying impeller rotation-speed C had an extremely signicant effect on Y 2 , also secondary to the machine ground speed B. And the superior combination of factor levels as A 2 B 2 C 2 was adopted through the comprehensive power energy consumption analysis. The verication test results indicated that under the optimized operation parameter combination, namely, when the crushing spindle rotation-speed A was 2100 r/min, the machine ground speed B was 0.8 m/s, and the conveying impeller rotation-speed C was 210 r/min, the mean value of inter-row straw uniformity Y 1 and seed-band width variation Y 2 were 90.85% and 10.73%, respectively, after machine operation. quality and agronomy

operation parameter combination, namely, when the crushing spindle rotation-speed A was 2100 r/min, the machine ground speed B was 0.8 m/s, and the conveying impeller rotation-speed C was 210 r/min, the mean value of inter-row straw uniformity Y 1 and seed-band width variation Y 2 were 90.85% and 10.73%, respectively, after machine operation.
Conclusion: It meets the requirements of operation quality and planting agronomy of relevant protective tillage machinery, and provides technical and equipment support for the research and development of similar straw crushing and no-tillage sowing.

Background
Crushing and returning to the eld is a universal and effective measure to solve the problem of surplus straw in modern large-scale farmland. While avoiding burning and polluting the environment, it also increases soil organic matter, improves soil structure, promotes microbial activity and the development of crop roots, and plays a positive role in increasing fertility and yield [1][2]. The no-till and less-till sowing technology as a normal operation method for implementing the concept of conservation tillage, it focuses on the main control target of protecting the ecological environment of the cultivated land, reducing the number of operation equipment landed the eld, decreasing soil erosion and structural damage, and preventing soil deserti cation and compaction. It is the current important production mode in the main grain production areas in the middle and lower reaches of the Yangtze River to improve production e ciency and economic bene ts [3].
As a typical rice-wheat rotation area in Jiangsu Province, the large amount of rice stubble is particularly prominent in the large-scale planting process, which hinders the smooth operation of fertilization and planting machines, destroys the good growth environment of crops, and restricts the strong promotion and application of no-tillage planting technology [4], especially the lack of straw crushing-returning technology and equipment that can meet the local agronomic requirements, has seriously affected the mechanization development of overall process for rice production and the safety of food production [5][6]. Therefore, it is particularly urgent to develop machinery and equipment for returning straw to the eld and planting with less tillage and no-tillage suitable for the rice-wheat rotation system.
In recent years, as the country continues to advocate the comprehensive utilization of straw resources and the advancement of land rotation and fallow strategies, more and more scholars at home and abroad have paid attention to the research and development of key technologies and equipment for straw crushing and no-tillage fertilization sowing [7][8][9]. ELFATIH [10] et al., in order to realize the reuse of crop residue as compost material, optimized and improved the feed-in straw crushing device designed to improve the straw crushing e ciency and productivity. Liu Peng [11][12] and other researches proposed a method of crushing and returning corn stalks to the eld in the form of different speed rollers and dynamic double supports. Through the design of pick-up and crushing blades and roller sliding support blades, the width and uniformity of broken straw scattering can be adjusted, and the pass rate of corn stalk crushing after operation is 92.58%. The 1JHL-2 straw deep burying and returning machine developed by Tian Yang et al. [13] can collect two ridges of straw and bury them in a ditch, so as to realize alternate deep burying of straw in ridge and ditch. SIDHU [14] and others developed a suitable 9row turbocharged wheat no-tillage planter with straw crushing and returning to the eld in rice stubble elds, which reduced fuel consumption costs, optimized the optimal planting period, and promoted direct wheat production in rice stubble elds. The 2BMFJ series no-tillage precision planter designed by Chen Haitao [15] used a lateral throwing method to collect the stubble on the side of the planting area, which solved the problems of di cult planting and slow rise of low temperature in the later period. Wang Weiwei et al. [16] designed an active straw shifting anti-blocking device to ensure the passability of the corn no-tillage planter when the wheat stubble is high and the straw is fully returned to the eld.
Throughout the current stage, the research on crop planting technology and equipment under the condition of straw mulching mainly adopts methods such as crushing and throwing mulching, ploughing and burying, mixed burying in soil, ditching and deep burying, and collecting straw on the side to accelerate the decomposition of straw in the eld. [17][18][19][20]. However, there are few researches on the compound operation technology of crushing all straws in the eld and collecting mulching between rows and sowing in the clean area [21][22][23]. In particular, there are few reports on the stability of operation quality, such as the uniformity of ridge pattern and the variation of seed band width.
Therefore, in view of the special planting environment of tight Crops for Rotation under the condition of full straw return in the rice-wheat rotation area in the middle and lower reaches of the Yangtze River, this study continued the technical concept of strip fertilization and seeding in "clean area" (no straw obstacle) [24][25][26], and developed a strip fertilization planter for straw crushing with back-throwing and interrowlaying. In a single operation, multiple production processes such as straw crushing, broken straw gathering and mulching, seed-bed arrangement, fertilization and sowing in clean area can be realized, which not only guaranteed the farming time under the rice-wheat rotation, but also realized the highquality and smooth no-tillage planting operation of the full amount of straw land. In addition, it can ensure the thermal insulation and moisture retention of the straw-covered ground surface, and the full contact between the seeds and the soil, and the phenomenon of di cult seedling emergence, weak seedlings and dead seedlings caused by straw mulching can be avoided. It would provide new technology and equipment for the realization of straw-free and high-quality machine sowing wheat operations in rice stubble elds, and provide new ideas for the development of conservation tillage concepts.

Methods
Planter structure Figure 1 illustrates the overall structure of the strip fertilization planter for straw crushing with backthrowing and interrow-laying, it is mainly composed of a rack, a suspension device, a transmission system, a straw crushing device, a broken-straw control device (post-throwing conveying device, diversion spreading device), a rotary tillage and soil covering device, and a strip fertilizing and seeding device. And the main technical parameters are shown in Table 1

Working principle
The developed strip fertilization planter adopted a three-point suspension connection. The output power of the tractor was transmitted to the left and right sides of the planter through a gearbox, by the gear transmission matched with the chain drive on the left side of the rack, the power of the impeller shaft for straw throwing was driven. The right side of the impeller shaft provided power for the rotary tiller shaft through a gear and chain drive, and the power for the straw crushing shaft was provided through a belt drive at the right side of the rack.
When working in the eld, the su cient driving for the whole machine was provided by the tractor connected to the power input of the gearbox at a standard speed of 720 r/min, and the matching required power to the crushing spindle and the rotary spindle was transmitted through the multi-stage wedge-belt.
The full coverage straw on the ground surface in rice stubble eld smoothly entered into the crushing cavity under the pressure of a depth-limiting roller, the high-speed and counter-rotating crushing movable blades picked up the straw within the working width with the help of centrifugal inertial air ow, and then cooperating with the array of xed blades on the top of the cavity, the straw was crushed. Then the broken straw entered with the high-speed air ow of the rotating blades, was captured by the straw throwing device (throwing impeller) in the cavity, and then accelerated to the rear spraying again. After crossing the soil rotary tillage device, under the reasonable guidance of the broken-straw regulating device, these broken straw were paved on both sides of the ground wheel in the non-sown region, forming 5 seeding belts without straw obstacles and 6 straw covering areas evenly spread between rows. A temporary straw-free cleaning zone was formed between the crushing device and the diversion device, where the rotary tillage, soil crushing, band-shaped fertilization and seeding operations were completed, avoiding the interference of straw on the soil rotary tillage and the seed bed arrangement, and creating a fertilization and seeding condition without the disturbance of straw barriers. Meanwhile, the necessary soil-covering suppression process would be completed subsequently, and nally a high-quality and smooth less-tillage sowing operations with full straw crushing and strip covering in rice stubble elds would be achieved.
Design of straw crushing device The straw crushing device is mainly composed of a blade spindle, a blade holder, a crushing blade group, a xed blade group and other parts, and its purpose is to pick up the rice straw and stubble on the ground surface and return them to the eld after crushing. In order to achieve the ideal straw picking and crushing effect, it is necessary for the crushing blades to be correctly selected and rationally arranged, and the blade spindle to meet a certain speed, so that the blade tip has a su ciently large linear velocity, and at the same time avoids violent vibration [27]. The con guration design of the crushing xed blade needs to match with the crushing swing blade, so that the straw is crushed into sections or bers of quali ed length, and a uniform straw ow is formed and sprayed to the rear of the broken-straw conveying cavity.

Structure design of crushing blade
Refer to the design experience of the research group on straw crushing devices [21,24], taking into account the strong crushing ability of the straight blade and the better picking effect of the L-shaped blade, combined with the agronomic requirements of wheat planting in the rice-wheat rotation area and the design requirements of this strip fertilization planter, a straight blade and two L-shaped blades are selected to form a combined swing blade (as shown in Figure 2), and the blades are positioned by sleeves to ensure that the blade set can be exibly ung and cut while avoiding axial shaking and mutual interference. The main design parameters are: 160mm ×60mm ×6mm (length ×width ×thickness), the bending angle is 120°, the cutting edge angle is 25°, and the material is 65Mn steel after quenching treatment to improve its strength, hardness and certain wear resistance, as well as to improve the straw crushing effect and the service life of the swing blades.
In order to be able to work in coordination with the broken straw conveying mechanism, the traditional Lshaped cutter was improved, and the sharp corners at both ends of the scimitar are removed, so that the broken straw can be smoothly thrown out of the surface of the crushing cutter, and then can be smoothly captured by the straw throwing device. This new cutter has both the crushing ability of the traditional straight blade and the pick-up capacity of the L-shaped blade. It has good symmetry, avoids the unbalanced inertia and the vibration of the whole machine, and can meet the working requirements of the straw crushing device and the broken-straw conveying mechanism.
Blades arrangement and spindle design improve the straw picking rate and crushing effect, but an excessive number of rotating blades can easily cause vibration of the whole machine and increase the power consumption of the planter. Refer to the same analysis method in "Agricultural Machinery Design Manual" and the literature [24], the arrangement of the movable blade set adopts the common double-helix staggered symmetry method, and is mounted on the blade seat welded on the surface of the blade roll through the pin hinge. The phase angle of the double helix is 180°, the distance between the adjacent blade groups on each helix is 140mm, and the circumferential interval is 72°, so as to ensure that the working area of the cutter is partially overlaps, and avoid missed picking and incomplete crushing. Because the effective working width of the whole machine is 2200mm, and a total of 32 movable blade sets are calculated according to this arrangement, Figure 3 shows the speci c arrangement.
In order to improve the straw picking and crushing performance of the strip fertilization planter, the crushing blade spindle was designed to rotate in the opposite direction (reverse), and the instantaneous support sliding cutting mode was formed between the movable blade group and the xed blade group, which puts forward certain requirements for the cutting speed of the movable blades (that is the rotation speed of the cutter spindle). The linear velocity of the crushing blade tip is a key parameter that affects the quality of straw crushing. Too high speed will increase the unbalance factor of the cutter roller itself, which is easy to cause vibration and increase power consumption. According to the working parameters of the existing machines [24], the linear velocity v g of the swing blade tip should meet 34-48 m/s, and the rotation radius r f of the cutter spindle should meet 240-350mm. Here, the design in this study v g =40m/s, r f =270mm. Combined with the requirements of the sowing speed in the region and the picking demand of the swing cutter on the ground straw, and comprehensively considering the eld surface unevenness and topographic undulations, the designed planter forward speed v=1m/s and the ground distance of the cutter tip determined by the depth-limiting device was selected h t =90mm. According to the following empirical calculation formula of the cutter spindle speed n: The cutter spindle speed n≥2070r/min was calculated. From the perspective of power balance and power consumption, on the premise of ensuring the straw crushing effect, the spindle rotation speed of the blades should be reduced as much as possible. Therefore, the rotation speed of the crushing spindle n=2100r/min was designed in this study.
Design of the regulating control device for broken straw The framework structure of the regulating control device for broken straw is shown in Figure 1, which is mainly composed of a post-throwing conveying device, a diversion strip-paving device, and a closed ( ) ( ) cavity for the broken straw ow formed by a bottom plate and a cover plate. During the working process, the picked up and crushed straws were thrown into the ow cavity under the action of inertial air ow, and then captured by the post-throwing conveying device that rotated in the opposite direction at a certain speed. Under the action of the rotating kinetic energy of the throwing impeller, the broken straw was further thrown backward to the distributary strip paving device, then owed to the outlet under the action of the air ow in the cavity, and were distributed by the guide device to both sides for strip stacking and forming a ridge, which collected and covered the non-sown strip-shaped area between the adjacent guide plates, forming a regular inter-row covered-straw belt (between rows).

Post-throwing conveying device
In order to achieve the smooth conveying effect for broken straw, the post-throwing conveying device must be highly coupled with the straw picking and crushing device. During the working process, the amount of straw thrown by the conveying device should be greater than or equal to its maximum feeding amount, so as to meet the operating e ciency and capture all the straw ejected from the straw crushing device [28]. At the same time, the throwing blades should provide su cient initial speed for the broken straw to ensure that the straw can be e ciently thrown to the preset diversion strip-paving device. Therefore, in order to ensure that the broken straw captured by the conveying device can be thrown backward smoothly and avoid the accumulation and blockage of the broken straw in the conveying cavity, the input and output volumetric ow rate (t/h) of the broken straw per unit time should meet the following relationship: Where, v d is the straw throwing speed, m/s; S d is the cross-sectional area of the throwing outlet, m 2 ; ρ is the straw bulk density, t/m 3 ; q is the straw amount per unit area, t/m 2 ; v is the machine forward operating speed, m/s; W is the working width, m.
During the post-throwing conveying process, the broken straw will be produced an implicative velocity with the rotation of the impeller, a relative velocity along the radial direction of the impeller vane will be generated under the action of centrifugal force, and the direction of the combined velocity is the direction in which the broken straw is thrown [29]. The composite motion analysis generated in the conveying process of the broken straw is shown in Figure 4, the broken straw follows the throwing impeller to rotate around the axis at a constant angular velocity ω (uniform circumferential motion), and the initial throwing velocity v d of any broken straw A is the compound velocity between the tangential velocity v T affected by the impeller vane and the radial velocity v r under the action of the inertia effect, then there is Where, δ is the included angle between the broken-straw throwing velocity and the tangential velocity, °; r A is the gyration radius of the broken straw A (distance from the rotation axis of O), m); n is the rotate speed of rotary impeller spindle, r/min.
Combined with the equations (2) and (3), it can be calculated that the necessary conditions to ensure the smooth post-throwing and conveying for the broken straw are as follows: With reference to relevant industry standards and literatures [24,29], the rice straw bulk density ρ = Referring to the agronomic requirements of wheat planting in the test area (rice-wheat rotation area in the middle and lower reaches of the Yangtze River) [24], the transverse width of the de ector plate is designed to be 185mm, and the adjacent diversion strip-paving devices are spaced 210mm apart and evenly distributed along the width, they are xed between the cover plate and the bottom plate at the outlet of the conveying cavity by bolts. According to the relevant design experience of the research team's previous research, discretize the movement process of broken straw particles on the diversion slope at a certain time t, establish the instantaneous motion differential equation of the broken straw, and analyze the corresponding law of motion. The speci c force balance equation and the dynamics analysis procedure are as seen the literature [21,23,24,26], so we won't repeat it here. Therefore, the half outward expansion angle of the diversion device designed in this study is 45°, the sliding-push curve of the center blade edge is a parabolic segment, the effective diversion length is 120mm, the diversion height is 250mm, and the installation clearance is 20mm, which can meet the requirements of the strip-paving operation for broken straw.

Design of the rotary tillage and soil covering device
The rotary tillage and soil covering device arranged the seed beds in the clean area without straw obstacle formed under the cavity bottom plate, which avoided the trouble of the large amount of straw residue jamming and winding, improved the inconsistent sowing depth caused by the un atness of the paddy planting eld, and enhanced the passability and operation quality of the planter. The speci c structure of the developed device is shown in Figure 6, in order to reduce the power loss caused by the unbalanced inertia of the rotary-tillage spindle during the soil rotary tillage process, the rotary tillage cutter set were designed to be arranged in a full-width spiral pattern within the operating range, and the cutter spindle is in shallow rotation in the forward positive direction. Combined with the overall structure of the developed planter and the requirements of wheat sowing depth in the regional rice stubble eld [21,22], the national standard IT195 rotary tillage scimitar was selected, and the tilling depth was adjustable between 60 and 100mm. At the same time, in order to reduce the weight of the whole machine, a hollow steel pipe with a diameter of 80mm and a wall thickness of 4mm was selected for the rotary-tillage cutter spindle.

Determination of rotary tillage parameters
In the rotary tillage process, the rotation speed of the cutter spindle directly affects the quality of soil crushing and the effect of seed bed nishing, and a reasonable rotation speed of the cutter spindle can also reduce the overall power consumption of the rotary tillage device. Its absolute motion is a compound motion of walking linear motion and self-rotating motion, the speci c process analysis is similar to the motion of cutting and crushing blade set in the previous studies (not further repeated here) [24,26]. When the rotary-tillage cutter roller rotates at angular velocity ω forward and the whole machine advances at velocity v, the motion equation of any point B(x, y) on the lateral cutting edge of the rotary tiller blade in unit time t can be expressed as: Where According to the literature [21], it can be known that the linear speed of the blade tip of the soil rotary tillage device is greater than 5m/s to achieve a good stubble breaking and shallow rotary-tillage effect. Substituting into Equation (5), ω > 25.12rad/s can be calculated, that is, the rotation speed of the rotarytillage cutter spindle >240r/min, in order to reduce unnecessary power consumption and consider the design margin, take the cutter spindle speed =250r/min.

Analysis of soil covering process
The rotary tillage and soil covering device uses the crushed soil thrown by the rotary-tillage cutter to cover the seed and fertilizer in layers and spatial positioning, so the soil throwing performance of the rotarytillage blades plays a key role in the effect of soil covering after sowing [27]. Therefore, it is necessary to analyze the motion characteristics of the broken soil particles thrown by rotary tillage. Similarly, the forward direction of the planter is the positive direction of the x-axis, the upward direction of the vertical ground is the positive direction of the y-axis, and the rotation center of the rotary tiller axis is the origin O. The coordinate system xOy as shown in Figure 7 is established.
In the process of soil crushing, considering the impact between the tangent plane of the rotary tillage cutter and the soil [30], when the rotary tiller cuts the soil particle C at a certain cutting angle α and linear velocity v b , a velocity coordinate x'Cy' with C as the origin is established. Then the proportional relationship between the normal and tangential components of the relative velocity of soil particle C in the dynamic coordinate system x'Cy' before and after the impact can be expressed as: Where, v 1n is the normal sub-velocity of the rotary tiller, m/s; v 2n is the normal sub-velocity of the soil particles after collision, m/s; v 1r is the tangential sub-velocity of the rotary tiller, m/s; v 2r is the tangential sub-velocity of the soil particles after collision, m/s; k is the recovery coe cient of soil particle collision, generally taken as 0.4; f is the instantaneous friction coe cient of soil particles, generally taken as 0.5; φ is the angle between the absolute movement velocity of the rotary tiller v b and the x-axis, °; α is the angle between the absolute movement velocity of the rotary tiller v b and the x' axis, °.
And the absolute velocity equation of soil particle C can be expressed as: Where, v c is the absolute velocity of soil particle C after collision, m/s; α' is the angle between the absolute velocity v c of the soil particle C and the x' axis after the collision, °.
If the air resistance was not taken into account, the particle C was idealized as an independent discrete body, neglecting the interaction with the surrounding soil, the continuity equation of the motion trajectory of the soil particle C, the rst derivative with respect to time t can be expressed as: x c = x 0 +v c tcos(φ − α + α ′ ) y c = y 0 +v c tsin(φ − α + α ′ ) − Where, (x 0 , y 0 ) is the initial position coordinates of the soil particles; g is the gravity acceleration, 9.8m/s 2 .
According to formula (8), it can be seen that the trajectory of soil particles thrown out by rotary tiller impact is parabolic, and when the particle throwing angle φ-α + α' is 45°, the distance the particles are thrown out is the farthest. Combined with the actual operating conditions of the developed planter and the corresponding parameter values are substituted, the maximum vertical height and horizontal displacement of the thrown soil can be calculated, which provides a design basis for arranging the seed dropping device and the relative position of the cavity bottom plate and the rotary tiller spindle.

Design of the transmission system
The power of the whole machine is provided by the output shaft of the tractor, which is divided into two transmission routes after the gearbox. The power is respectively transmitted to the straw crushing device, the broken-straw conveying device and the rotary tillage soil covering device through the multi-ribbed belt transmission, and the transmission route is shown in Figure 8.
According to the system transmission route shown in Figure 8, the transmission ratios of the developed planter structure are respectively calculated as: Where, i A is the total transmission ratio of the straw crushing device; i B is the total transmission ratio of the broken-straw conveying device; i C is the total transmission ratio of the rotary-tillage soil covering device.
Combined with the speed analysis requirements of the key components mentioned above, the speed of the crushing spindle is 2100r/min, the speed of the conveying impeller is 210r/min, and the speed of the rotary-tillage spindle is 250r/min. Considering the power consumption of the whole machine, the PTO output shaft speed of the tractor is determined to be 720r/min, then i A =0.34, i B =3.43, and i C =2.88 can be calculated respectively. In addition, comprehensive consideration of the actual size, structural layout, operating environment, agronomic requirements and other factors of the complete machine transmission system, scienti c and reasonable allocation of the transmission ratio of each branch are needed, depending on the actual selection situation.

Calculation of the matching power
In the operation process of the developed strip fertilization planter for straw crushing with back-throwing and interrow-laying, when the tractor is used as a traction machine, the power consumption of the whole { Page 14/33 machine can be approximated as the sum of the power consumed by the tractor to overcome the friction resistance, the traction resistance and the load [31], and the power consumption of the wear and tear between the parts (much less than the above-mentioned main consumption) is ignored. Then the empirical formula for the maximum power output of the tractor PTO can be expressed as: Where, P is the PTO output power, kW; k is the safety factor, generally 1.1-1.2, the value of k = 1.2 in this study; P n is the average power consumption of the load, kW; F n is the average traction resistance of the planter, N. Compared with ditching and deep rotary-tilling, the magnitude of the traction resistance is smaller, which is ignored here; m is the mass of the whole machine, kg. Combined with the technical parameters in Table 1 and the rated parameters of the tractor, here m = 5330kg is selected; g is the acceleration of gravity, m/s 2 , here g = 10 m/s 2 is taken; f is the rolling friction coe cient between the whole machine and the ground, the value f =0.7 in this study; v is the walking speed, km/h, usually the eld operation speed of the whole machine v =0.8m/s, that is, v =2.88km/h.
Among them, the power consumption of the tractor PTO output for the load mainly includes the power consumed by the straw crushing operation P n1 and the power consumed by the rotary tillage and soil covering operation P n2 , while the power consumption required by the broken-straw throwing impeller is relatively small, which can be ignored for simpli cation, so the load power consumed of the whole machine can be calculated according to the following formula: P n = P n1 + P n2 P n1 = k t Bh t P n2 = k r bh r

11
Where, k t is the soil speci c resistance of the straw crushing device, N/cm 2 , generally 5N/cm 2 is taken here; B is the width of the crushing operation, cm, according to the design parameters, this study takes B=220cm; h t is the mulching depth of broken straw, cm, according to the design requirements, the value is h t =13cm; k r is the speci c resistance of rotary tillage, N/cm 2 , generally 10 N/cm 2 is selected for shallow rotary tillage; b is the working width of the rotary tillage device, cm, according to the design parameters, b=220cm is taken here; h r is the rotary tillage depth of seed belt, cm, value h r =6cm is selected here.
Substituting various parameters into equations (10) and (11) for the selection of technical parameters for traction equipment.

Analysis of eld performance test
The experiments were carried out at the Baima Teaching and Research Base of Nanjing Agricultural University, Lishui District, Nanjing City, Jiangsu Province in November 2020. The rst crop of rice straw in the test plot was returned to the eld in full amount after the machine harvest, and the variety was Nanjing 9108, which was planted within the full operation width. The measured straw mulch amount was 2.03kg/m 2 , the moisture content was 19.4%, the average stubble height was >200mm, the soil rmness at the depth of 10-15cm was 18.9Mpa, and the soil moisture content was 19.3%. And the tractor Dongfeng 1404 was used.
To better evaluate the overall operation effect of the developed strip fertilization planter for straw crushing with back-throwing and interrow-laying, the main working parameters that affect the quality of the broken straw strip-paving and the growth of the seed belt crop were selected: the speed of the crushing spindle A, the walking speed of the whole machine B, the speed of the conveying impeller C as the test factors, and the straw mulching uniformity between rows was used as the evaluation index Y 1 to characterize the effect of straw mulching, the seed-belt width variability was used as the evaluation index Y 2 to characterize the quality of the seed belt, so the eld performance tests of the fertilizing planter were carried out. Referring to the similar literature [16, 18, 24] on the operating performance research of straw crushing and returning to the eld and no-tillage planter, combined with the preliminary pre-test results of the research group and the actual operation experience basis, the appropriate factors and levels were selected, as shown in Table 2. A 3-factor 3-level orthogonal performance test (L 9 (3 4 )) was designed to obtain the best overall machine working parameters and operating conditions.  [35]. Figure 9 is the eld performance test of the whole machine.
During the tests, the corresponding crushing spindle speed A, machine walking speed B, and conveying impeller speed C were adjusted in each single test according to the design scheme. The developed strip fertilization planter was pulled by the tractor, after waiting for the planter calibration and the stable working conditions, the uniformity coe cient Y 1 of the straw mulching between rows and the variation coe cient Y 2 of the seed-belt width under each parameter combination condition were measured, respectively, to analyze and evaluate the effect of back-throwing and interrow-laying of the strip fertilization planter. After a single test, 10 collection points with an area of 100mm×100mm (a total of 60 collection points) were randomly selected at equal intervals on a diagonal line in each row of the 6 straw mulching areas within the effective working width (2.2m), and the broken straw mass w i of each collection point was weighed successively. Similarly, 10 collection points (50 collection points in total) were randomly selected from 5 clean-zone seed belts within the effective working width (2.2m), and a tape measure was used to measure seed belt width W j of each collection point successively. Each group of experiments was repeated 3 times and the average value was taken, the calculation formulas of the corresponding test evaluation indexes for the uniformity of straw mulching between rows Y 1 and the variability of seed-belt width Y 2 were calculated as follows:

Results
According to the above-mentioned test method and design scheme, the results of the orthogonal performance test of the developed planter were shown in Table 3, and the range analysis and variance analysis of the test results were conducted (shown in Table 4). From the numerical analysis of the range R of various factors in Table 3, it can be seen that for different evaluation indexes Y 1 and Y 2 , the effects of the test factor A, B, and C are signi cantly different. For the evaluation index Y 1 , the signi cance order of the factors is A>B>C, indicating that the speed of the crushing spindle has the greatest in uence on the uniformity of straw mulching Y 1 , followed by the walking speed of the whole machine, the speed of the conveying impeller is the least, and the optimal factor-level combination is A 3 B 2 C 2 . For the evaluation index Y 2 , the signi cance order of each factor is C>B>A, indicating that the speed of the conveying impeller has the greatest in uence on the variability of the seed-belt width Y 2 , the walking speed of the whole machine is the second, the speed of the crushing spindle has the least impact, and the optimal combination of factor levels is A 1 B 2 C 2 .

Tab.3 Results of orthogonal test
Tab.4 Analysis of variance According to the variance analysis results in Table 4, it can be seen from the variance analysis of evaluation index Y 1 that F A >F B >F C , indicating that the in uence of factor A on index Y 1 is extremely signi cant, the in uence of factor B is signi cant, and the in uence of factor C is slight. Through the variance analysis of the evaluation index Y 2 , it can be seen that there is F C >F B >F A , indicating that factor C has an extremely signi cant impact on index Y 2 , factor B has a signi cant impact, and factor A has a minor impact, which is consistent with the range analysis results above-mentioned. Combining the results of range and variance analysis, it can be seen that the in uence of various test factors (A, B and C) on different evaluation indexes (Y 1 , Y 2 ) is different in signi cance, and the corresponding optimal factorlevel combination is also different. When the evaluation result was given priority to index Y 1 , factors A and B had signi cant in uence on index Y 1 , and factor C had no signi cant in uence, while factor C had an extremely signi cant in uence on index Y 2 , and the factor-level combination A 3 B 2 C 2 was the best.
When index Y 2 was given priority, factor C and B had signi cant in uence on index Y 2 , factor A had no signi cant in uence, while factor A had an extremely signi cant in uence on index Y 1 , and the factorlevel combination A 1 B 2 C 2 was the best.

Discussion
Further analysis showed that the evaluation index Y 1 increased with the increase of the test factor A, indicating that the uniformity of the inter-row straw mulching could be improved by increasing the rotating speed of the crushing spindle. The higher the speed of the crushing spindle, the better the straw crushing effect, and the greater the uniformity coe cient of the broken-straw inter-row paving. However, the excessive crushing spindle speed will bring unnecessary power consumption, so it is necessary to balance the appropriate crushing spindle speed to match the power requirements of the whole planter on the basis of meeting the requirements of straw crushing and straw mulching uniformity. The index Y 1 showed a trend of rst increasing and then decreasing with the increase of factor B (which was parabolic shape), and the peak value appeared at B 2 , indicating that too small or too large machine walking speed will cause Y 1 to increase. his is because the slower the machine travels, the more likely it is that the smashed straw will be intermittent during the strip paving process, which leads to an increase in the uniformity coe cient of the mulching straw per unit area. However, the larger the walking speed, the easier the broken-straw to be blocked at the diversion point of the regulating control device in a limited time, which is not conducive to the smooth sliding of the broken straw to both sides, and it will also increase the uniformity coe cient of the straw mulching. Factor C has no signi cant in uence on index Y 1 , so detailed analysis will not be made here.
The evaluation index Y 2 presented a trend of rst decreasing and then increasing with the increase of test factor C (which was concave parabola), the peak value appeared at C 2 , indicating that too small or too large conveying impeller speed will cause Y 2 to increase. Because the impeller speed is too slow, a large amount of broken straw picked up and crushed by the straw crushing device is concentrated at the feed inlet of the conveying impeller, causing a lot of clogging of the broken straw. However, if the impeller rotating speed is too high, the conveying impeller will concentrate a large amount of broken straw at the de ector plate of the diversion control device, which will not be able to smoothly diverging and strippaving in a short period of time, and the sparse and scattered laying of broken-straw will increase the variation coe cient Y 2 of the seed-belt width. The index Y 2 is also presented a trend of rst decreasing and then increasing with the increase of factor B, the peak value appeared in B 2 , indicating that appropriately increasing the planter walking speed within a certain range is bene cial to the effect of broken-straw distribution and laying, and improve the variability of the seed belt width. While when the walking speed exceeds a certain value, the broken-straw that is going to be diverging and strip-paving cannot slip off in a fast and short time, and will be scraped or pushed by the regulating control device to a certain extent, destroying the ridge shape of straw mulching between rows, resulting in a gradual increase in the variation coe cient of the seed belt width. Similarly, the in uence of factor A on the index Y 2 is not signi cant, and no detailed analysis will be made here.
Therefore, combining the evaluation index Y 1 (the uniformity coe cient of the straw mulching between rows) and Y 2 (the variation coe cient of the seed-belt width), it can be found that the best level of factor A that affects index Y 1 the most signi cant is A 3 , and the best level of factor C that affects index Y 2 the most signi cant is C 2 , and the optimal factor-level combination is A 3 B 2 C 2 . Considering from the perspective of the machine power consumption and the clean energy, under the condition of satisfying the straw crushing effect, ensuring certain straw mulching uniformity and seed-belt width variability, it needs to minimize the power consumption and reduce the rotation speed of the crushing spindle, there is a relatively optimal combination of factor-level as A 2 B 2 C 2 , which did not appear in the orthogonal test scheme. Therefore, a corresponding eld veri cation test is designed to evaluate the broken-straw strippaving quality and machine operation effect under the two factor-level combination

Test veri cation and analysis
In order to verify the rationality of the optimal factor-level combinations obtained by the above orthogonal performance test, a eld veri cation test of no-tillage sowing wheat in the rice stubble eld was carried out. Before a single test, the operation parameters of the whole machine were adjusted to the best and better factor-level combinations A 3 B 2 C 2 and A 2 B 2 C 2 . The test method was consistent with that in section 3.3, and the uniformity coe cient Y 1 of the inter-row straw mulching and the variation coe cient Y 2 of the seed-belt width under each factor-level combination were determined respectively. Each test group was repeated 3 times and the average value was taken, and a total of 6 repetitive tests were conducted in each group. The eld test scenarios and effects were shown in Figure 10, and the test results were shown in Table 5. Combined with the eld operation effect and the veri cation test results, it can be seen that the developed strip fertilization planter for straw crushing with back-throwing and interrow-laying had good passability and stability, and the full mass straw in the rice stubble eld was completely crushed and laid in a regular manner on both sides of the diversion device. For the factor-level combination A 3 B 2 C 2 , the average uniformity coe cient of the straw mulching Y 1 was 92.06%, and the average variation coe cient of the seed belt width Y 2 was 9.66%. For the factor-level combination A 2 B 2 C 2 , the average uniformity coe cient of the straw mulching Y 1 was 90.85%, and the average variation coe cient of the seed belt width Y 2 was 10.73%. All the working quality could meet the technical standards of the relevant agricultural machinery industry technical standards and the local agronomic production requirements. Therefore, for the consideration of the machine power consumption and long-term economic cost, the optimal factor-level combination of the operation parameters A 2 B 2 C 2 was selected, that is, the rotation speed of the crushing spindle was 2100 r/min, the walking speed of the whole machine was 0.8 m/s, and the rotation speed of the conveying impeller was 210 r/min. It can effectively improve the operating performance of the developed strip fertilization planter for straw crushing with back-throwing and interrow-laying, the uniformity of the broken straw inter-row mulching is better, and the variability of the seed-belt width is minor, which provides technical reference for realizing the high quality and smooth no-tillage sowing compound operation in the clean area.

Conclusions
This study continued the idea of strip fertilization and planting in 'clean area', a strip fertilization planter for straw crushing with back-throwing and interrow-laying was developed, the main factors that affect the uniformity of the broken straw mulching between rows and the variation of the seed-belt width were theoretically analyzed, and the optimal combination of operating parameters was determined to give play to the best operating performance of the strip fertilization planter.
The performance test results showed that through the range and variance analysis, it is clear that the signi cance of the evaluation indexes Y 1 and Y 2 were in the order of A, B, C and C, A, B, respectively, and the optimal factor-level combination scheme was A 3 B 2 C 2 . Comprehensively considering the power consumption and environmental protection effects, the better factor-level combination scheme was A 2 B 2 C 2 , on the basis of ensuring operation requirements and agronomic requirements The eld veri cation test results showed that under the optimized operating parameter combination, the developed strip fertilization planter had good passability and high stability, and the factor-level combination A 2 B 2 C 2 could save a certain amount of power consumption while meeting relevant industry technical standards and production quality requirements. When the rotation speed of the crushing spindle was 2100 r/min, the walking speed of the whole machine was 0.8 m/s, and the rotation speed of the conveying impeller was 210 r/min, the average uniformity coe cient of the straw mulching Y 1 was 90.85%, and the average variation coe cient of the seed belt width Y 2 was 10.73%, which achieved better strip-paving quality of broken straw and arrangement effect of seed bed.

Declarations
Availability of data and materials The datasets supporting the conclusions of this article are included within the article and its additional les. cover plate; 11. Throwing blower; 12. Bench; 13. Fertilizing and sowing device; 14. Transmission system; 15. Suspension system Figure 2 Structural diagram of the crushing blades Scene picture of performance test Figure 10 Picture of eld validation test and operation effect