# Structure Design and Bearing Capacity Analysis for Crawler Chassis of Rice Combine Harvester

Authors: Zhong Tang; Hui Ren; Xiyao Li; Xin Liu; Biao Zhang
Journal: Complexity
 (2020)

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## Abstract

Due to the current unstable travel performance and poor driving maneuverability of rice combine harvester crawler chassis with high load in the rice field, the driver’s standard sitting posture model was developed by analyzing the handling of the crawler chassis driving control panel. Based on this model, the joystick length and cab manipulation space layout were designed. The Finite Element Software was used to develop the loading and restraining model of the chassis frame, and then the structural characteristics and bearing capacity of the crawler chassis were analyzed. The high-bearing running stability and the rationality of operating force of the joystick of rice combine harvester crawler chassis designed in this paper through experiments were verified by experiments. The results showed that when the crawler chassis of rice combine harvester bears a load of 3.5 t, the driving speed is relatively stable in the three speed ranges of 1 m/s, 1.5 m/s, and 2 m/s, and the maximum variance of driving speed variation is 5.022 × 10−4. The actual average operating force of each operating lever on the crawler chassis ranges from 30.36 to 42.71 N, and the operating force of each operating lever is suitable for 95% of Chinese adult male operators. The research results provide a good method and reference for the future development of the crawler chassis structure of rice combine harvester.


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## Body

## 1. Introduction

In the process of rice harvesting, rice combine harvester, as an important tool to improve the harvest efficiency of rice, can effectively reduce the labor intensity of farmers and improve the harvest efficiency [1]. In addition to the higher requirements on the working performance of the working device, the rice harvesting also puts forward higher requirements on the field pass ability, operational reliability, and operation simplicity of the crawler chassis [2]. At present, there are many kinds of crawler rice combine harvesters in China, but the cab is lack of ergonomics design, and the driving control structure is poor in adaptability. Therefore, it is urgent to develop the cab and chassis structure of the rice combine harvester which is suitable for the majority of adult male operators in China.When crawler chassis is driving in the field, problems such as poor crossing performance and unstable walking under high load due to the interaction between crawler and soil often exist [3]. To this end, Sojka and Cornak proposed the theoretical mathematical model of the vibration problem of tracked vehicle by studying the interaction between the chassis components and the vehicle body during the running of the tracked vehicle. The research provides a reliable theoretical basis to design the track of the vibration-damping structure [4]. Liu et al. proposed a wheel-rail adjustable steering mechanism based on steering mechanism and parallel quadrilateral mechanism, determined key variable and calculation method of steering error, and designed an adjustable wheel-rail agricultural chassis to overcome the defects of poor steering performance and flexibility of agricultural chassis [5]. Sutisna et al. adopted the vehicle model of the rice combine harvester with crawler differential steering to study the steering control performance of the rice combine harvester [6]. Lu and Lu designed a differentia reversal to caterpillar chassis; the caterpillar chassis braking system has a simple structure, has flexible use, assemble, and disassemble because it has good braking effect, and solves the problem of small crawler chassis braking better [7]. To improve the caterpillar chassis walking and brake performance, Li et al., designed a chassis and gearbox mechanism that can realize three kinds of steering modes, such as differential reverse steering, differential steering, and single-side brake steering. Their results improved the flexibility of the combine harvester in the field, and overcome the defects of large steering area and large steering resistance caused by the single-side braking method of the traditional crawler chassis [8]. Li et al. proposed a new hydraulic viscous drive (HVD) power drive system to realize stepless speed creep without affecting the service life of the combine harvester drive system, improving the driving comfort of the combine harvester [9]. Xia and Sun proposed a new type of stepless transmission (CVT) system, which adopts a stepless speed-regulating power cycle hydraulic mechanical transmission structure, thus obtaining a large torque ratio at zero speed ratio and improving the transmission efficiency of the rice combine harvester [10]. The crawler chassis has always been the focus of research by many scholars. A variety of crawler chassis structures have been developed for different walking environments and chassis structures. However, there are few reports on the development and design of the rice combine harvester.There are many research studies on caterpillar chassis of combine harvester in vibration and braking ability. However, the design still lacks relevant theories and data of ergonomics design, which leads to some problems such as poor operating comfort. In view of the design of a control layout of crawler chassis is unreasonable and prone to problems such as driving fatigue and misoperation, Lidiane and Joao through the ergonomics work analysis (EWA) and Wisner’s human body hypothesis for Australia compared with the sugarcane harvesting machinery and its operation in Brazil, and the mechanical structure and the change of the operating space caused by different human variable are proposed [11]. Qiu et al. conducted a survey of the satisfaction of tractor drivers on the function and interface usability of driving operations [12]. Han et al. analyzed the characteristics of the manual take-up operation, designed the structure of the edible sunflower harvester, analyzed the travel distance of rod stroke, and designed the rod length variable in combination with transmission angle conditions [13]. Lee et al. designed a small combine harvester based on Korean human variables, making the operating space suitable for most Korean operators [14]. In order to improve the manipulator’s handling of agricultural machinery, Wang et al. designed the joystick length and maneuvering space layout and completed the optimal design of the combine harvester based on driving comfort through the driver’s sitting posture simulation and control panel access control sexual analysis [15]. In order to solve the problem of poor performance of agricultural machinery in the orchard operation in hilly areas, Wang et al. and other researchers have designed a triangular track-type orchard power chassis with simple operation, good stability, and climbing performance [16].At present, there are many research studies on crawler chassis, but the existing crawler chassis still has problems such as poor passability in rice fields, unstable operation at high load, and poor driving maneuverability. For this reason, this paper completes various operations through ergonomics. Design of the control space layout of rod and cab is completed by mechanical analysis to complete the design of the track-related variables. After the meshing, the Finite Element Analysis of the chassis frame is carried out, and the bearing capacity is theoretically verified. By comparing and analyzing the data of high-load linear driving test, man-machine test of operating force of the operating rod, and theoretical design value, the rationality of crawler chassis of rice combine harvester designed in this paper is verified in terms of bearing capacity and maneuverability.


## 2. Material and Methods

### 2.1. Overall Structure and Working Principle of Crawler Chassis

The crawler chassis has good field passability and overall load-bearing ability. The rice combine harvester crawler chassis is mainly made of rubber track. The crawler chassis adopts the three-layer chassis structure, which can ensure the stability of the whole machine under the condition of large load [17]. A cab is designed on the crawler chassis of the rice combine harvester, which can realize the walking and steering control of the crawler chassis. Crawler chassis can be used for walking on complicated working ground such as rice field, and various crawler rice combine harvesters can be mounted to realize field operation. Crawler chassis of rice combine harvester designed in this paper is mainly composed of three major parts: rubber track, combine harvester cab, and chassis frame. The crawler chassis structure is shown in Figure 1.Figure 1
Schematic diagram of crawler chassis of rice combine harvester.The crawler chassis of rice combine harvester is a “four wheels and one belt” structure, which is mainly composed of a driving wheel, thrust wheels, a guiding wheel, a towing wheel or a tensioning wheel, and a crawler track [18, 19]. The structure of the crawler chassis “four wheels and one belt” is shown in Figure 2.Figure 2
Structure of the “four wheels and one belt.”When the crawler chassis is walking in field, the driving wheel is rolled up from the rear by the engagement between the gear teeth on the driving wheel and the track chain under the action of the driving torque of the speed reducer. The adhesion of the track under the thrust wheel to the ground forces the drive wheel to wind up the track, and the guide pulley lays the track to ground, allowing the body to run forward along the track.


### 2.2. Design of Main Variable of Crawler Chassis

Track support lengthL, track gauge B, and track board hanging width b shall be reasonably matched to meet the requirements of grounding pressure ratio, adhesion performance, and turning performance. The initial weight of rice combine harvester is 4 t. According to the research results of reference [20], the empirical Equation for calculating crawler chassis is shown as follows:(1)L0≈1.07G3,(2)L≈L0+0.67h0,where L0 is the grounding length, the unit is m; h0 is the crawler height, the unit is m; and G is the weight of the machine, the unit is t.LetG = 4 t into equation (1) give L0 = 1700m; taking h0 as 470 mm and substituting equation (2) gives L = 1864.5 mm. The ratio of the track grounding length L0 to the gauge B is generally between 1.2 and 1.4, and the boarding width b and the grounding length L0 are generally between 0.18 and 0.22. From the abovementioned ratio relationship, B = 1307 mm and b = 340 mm.The track pitcht0 and the number of drive wheel teeth z should meet the strength and stiffness requirements. In this case, try to choose a small value to reduce the track height.According to the relationship between the pitch and the weight of the whole machine,(3)t0=15∼17.50.001G4,(4)L′≈2L0+zt02+12∼23t0+2Δ,where L′is the full length of the track, the unit is mm; T0 is track pitch, the unit is mm; and z is the number of driving wheel teeth.SubstituteG = 4 t into equation (3), then t0 = 127 mm; take z = 6, substitute t0 = 127 mm and L0 = 1700 mm into equation (4), and then L′ = 3906.1 mm.According to the research results of reference [21], the average ground pressure ratio of crawler chassis is usually 50∼58 kpa, which is an important technical variable of crawler chassis. It directly determines the passability and stability of crawler chassis structure and is also a decisive condition for the research on the adhesion torque between crawler and ground. In this paper, 50 kpa is adopted, and the track ground area is determined by the track load quality and average ground pressure, as shown in the following equation:(5)A≥G′P,(6)A=2bL0,where b is the track board hanging width, the unit is m; G′ is chassis bearing weight, the unit is N; P is the average grounding voltage ratio, the unit is pa; and A is the ground area, the unit is m2.LetG′=Gg=9.8G=39200Nbe substituted into equation (5), and bL0≥0.392 m2 can be obtained by combining the two equations (5) and (6).According to the calculated and actual data, the track hanging plate widthb is 340 mm, the grounding length L0 is 1700 mm, then the total length L′ is 3900 mm, and the full-load average grounding pressure ratio P is 33.9 kpa.The drive wheel segment circle radiusr is an important variable to calculate the performance requirements of crawler travelling devices, such as Mr and Max. The design variables of the driving wheel are mainly determined by transfer power and travel speed. When designing the belt pulley, adding the number of gears can determine the meshing tooth number when the track moves correspondingly, so as to ensure the meshing uniformity of the track and improve the overall dynamic performance. However, it also increases the overall size of the drive wheels and adds height to the chassis. Therefore, the number of driving wheel teeth z in this paper is 6. Then, the calculation equation of the drive wheel segment circle radius r is as follows:(7)D=t0sin180/z,(8)r=D2,where D is the drive wheel diameter, the unit is mm, and r is the drive wheel pitch circle radius, the unit is mm.Letz = 6 and substitute t0 = 127 mm into equation (7) to get D = 254 mm. Then, substitute into equation (8) to get r = 127 mm.


### 2.3. Development and Design of Rice Combine Harvester Cab

The cab of crawler chassis is mainly composed of a driving seat, a central bedplate, a side control panel, and various joysticks. The crawler chassis of track designed in this paper is shown in Figure3. From the Chinese adult male body size and sitting size, the size, stroke, and steering angle of the operating levers are reasonably designed. Based on the ergonomics theory, the relative position of the joystick suitable for the majority of Chinese adult male operators was designed, and the layout optimization analysis of human-machine control interface cab was carried out [22, 23].Figure 3
Top view of the combine harvester cab.


#### 2.3.1. Design of Operating Lever

The operating levers of the rice combine harvester are divided into two categories according to their structure and principle, small switch stroke, and large switch stroke. The small switch stroke is like the reel lever and the header control lever [24]. The structure of the lever and the principle of simplified operating lever are shown in Figure 4.Figure 4
Small switch travel of the reel and principles of the operating lever.By querying the relevant variable of the existing valve body, it can be known that the stroke required for the valve body switch connected with the unloading clutch lever, reel operating lever, and brake lever is 10 mm, and the stroke of the valve body switch connected to the forward and backward operating lever is 20 mm. The valve body switch connected to the shift lever is required to have a stroke of plus or minus 35 mm, the stroke of the valve body switch connected to the cutting table integrated joystick is 20 mm, and the stroke of the valve body switch connected to the harvesting device joystick is 80 mm.Structure of the rod shown in left part of Figure4 is simplified to the linkage mechanism shown in right part of Figure 4. Through the analysis of the model, the required manipulation angle of the rod member when the corresponding valve body switch is completed can be obtained. Manipulate the amount of displacement.Set the length of theCD rod up and down displacement DD', that is, the switch stroke is c, and set the rotation angle of the rod during the work is θ, BC = l2, CD = l3, ∠ABA′＝∠CBC′ = θ, where θ is the designed.In ΔCBC', the triangle is an isosceles triangle, where BC=BC',(9)HD′=l3−l2sinθ+c,2l22cosθ+2l2l3+csinθ=2l22+c2+2l3c.According to the weight value and priority of the human-machine interface of the rice combine harvester, we should pay more attention to the design of the joystick in the cab. According to relevant studies [25], priority sequence and weight values of main joystick parts in each cab are shown in Table 1. We can conduct comparative analysis on the rationality of theoretical design of the joystick based on the priority of joystick.Table 1
Weight value and priority of each component of human-machine interface of combine harvester cab.
No.
The evaluation object
Frequency of utilization %
Priority order
1
Unloading clutch operating lever
3
4
Reel operating lever
2
Forward and backward operating lever
80
1
3
Shift lever
5
3
4
Cutting table integrated joystick
10
2
5
Harvesting device joystick
1
5
6
Brake lever
1
6In order to analyze and design the operating force of operating levers later, the switch strokec of the bar members and the length l2 and l3 of the operating levers can be obtained from the previous paragraph. By putting them into equation (9), the rotation angle θ of the main operating levers in the cab can be calculated.In the case of designingl2, l3, θ, and other variable of each lever, the length of the hand holding part of each lever is set according to the simplified mechanical analysis of the operation process of the joystick and the optimal operation force of the hand. Relevant studies show that the minimum operating force of the back of the human hand is 10N, and if the operating force of the hand is less than 10 N, the controllability is not good. The maximum front and rear operating force of the hand is 130 N, and when the operating force is greater than 130 N, the controllability exceeds the 95th percentile adult male hand operating force in China. According to the research results of reference [26], the optimal average arm operating force of Chinese adults is 40N, the maximum left-right operating force of a handle is 90 N, and the optimal average arm operating force from left to right is 30 N. Based on the following mechanical analysis, we complete the design of various joystick lengths.Since the operation process is a variable force process, in order to simplify the calculation, the calculation is performed at two moments when the joystick is moved to the intermediate position and the final position. The direction of the operating force is always perpendicular to the rod, and the position at every moment between the movements to the final state is simplified to the equilibrium state. The frictional resistancef only exists in uniform rod BC, and take f for 80 N. Let rotation angle be θ, operating force F1, the bottom connection body bar stress F2, the length of lever AB l1, the length of lever BC l2, the length of lever CD l3, the switch travel movement GD c, and the length of lever BJ l4. Let ∠BC'J = θ1, ∠BCC' = θ2, ∠CD'C' = θ3, and ∠CC'D = θ4. Among them operating force F1 of each operating lever is desired.According to Figure4, it can be known from the moment balance that(10)F1⋅l1=F2⋅l4+f⋅l2.From the isosceles triangle BCC', we know that(11)∠BC′C=∠BCC′=θ2=180−θ2,θ4=θ2.In the triangle CDF, according to the law of cosines, we can know that(12)θ3=arccos2l32+c2+2l3⋅c−4l22sin2θ/22l32+2l3⋅c.In the triangleBC'J, l4=l2⋅sinθ1.From equations (10) and (12), we can obtain(13)F1=F2⋅l4l1+f⋅l2l1=F2⋅l2⋅sin180−θ/2−arccos2l32+c2+2l3⋅c−4l22sin2θ/2/2l32+2l3⋅c+θ/2+f⋅l2l1.The componentF3 of F2 in the vertical direction is the force required to open the valve body, so F3=F2 cosθ3. The magnitude of this value varies according to the valve body. The relevant data can be seen that the required force F3 of the switch valve body is 40 N. Thereby, the specific value of each joystick F2 can be calculated, and the design value of the length l1 of the joystick is finally completed. The results of the overall joystick design are shown in Table 2.Table 2
Main dimensions of Chinese adult male human body (mm).
No.
Percentile
Height
Weight
Upper arm length
Forearm length
Thigh length
Shank length
1
5
1583
48
289
216
428
338
2
50
1678
59
313
237
465
369
3
95
1775
75
338
258
505
403


#### 2.3.2. Cab Maneuvering Space Layout

Since most of the combine harvester operators are male, the overall design of the cab is based on the body size of Chinese adult males, but the design method of this paper is also applicable to the cab of female operators. Chinese adult body size is the main source of design data and size reference for this design [27]. The main dimensions of male human body in the 5th, 50th, and 95th percentiles of Chinese adult human body are shown in Table 2, and the sitting variable of the male human body in the 5th, 50th, and 95th percentiles of Chinese adult human body are shown in Table 3.Table 3
Sitting variable of Chinese adult male human body (mm).
No
Percentile
Sitting height
Sitting position cervical high point
Sitting eye height
Sitting shoulder high
Sitting cubits high
Sitting thigh thick
Sitting knee height
Leg to foot height
Hip and knee distance
Sitting leg length
1
5
858
615
749
557
228
112
456
383
515
921
2
50
908
657
798
598
263
130
493
413
554
992
3
95
947
691
836
631
291
146
523
439
585
1046In the actual design calculation, due to the influence of the workers’ clothing, shoes, posture, and psychological factors, it is necessary to add an appropriate amount of correction to the design. The shoe wear correction amount is increased by 25 mm based on the measured value, and the dressing correction amount is increased, such as the hip width, by 15 mm on the basis of the measurement. In the actual situation, the operator mostly operates in a relaxed state, so a certain amount of correction should be subtracted from the standard of standing height and eye height.According to the principle of ergonomics, the range of the upper limbs determines the range of the working space in the sitting position. Also, the comfortable working range changes with the height of the working surface, the distance of the hand from the center line of the human body, and the height of the hand. In addition, the range will be affected by the dress. Tables2 and 3 can be designed, as shown in Figure 5, for the 95th percentile adult upper limb horizontal working area in China. The design of the combine harvester cab has a design space of 1400 × 1100 × 1350 cuboid.Figure 5
Low-speed full-load stress-strain diagram. (a) Equivalent stress diagram at low speed and full load. (b) Strain distribution at low speed and full load.
(a)
(b)


### 2.4. Chassis Frame Design

#### 2.4.1. Chassis Frame Structure and Bearing Variables

The chassis frame consists of four main beams, five main longitudinal beams, and auxiliary beams supporting other components, which are placed at the fulcrum of the main load such as the grain bin, threshing drum, engine, and bridge [28]. The chassis frame is made of 30 × 30 mm, 40 × 40 mm, and 40 × 60 mm square tubes and rectangular tubes of different specifications. The thickness of the chassis is 2 mm, 3 mm, 4 mm, and 6 mm, and the connecting plate is used for fixing and strengthening. The entire rack is 3.807 m long, 2.163 m wide, and 1.036 m high.The chassis frame adopts a 3-layer structure. The upper layer mainly carries the weight of the cab. The frame structure is used to increase the contact area with the cab so that the force is even, the stress and strain of the frame are reduced, and the bearing performance is improved. The frame is used for placing the hydraulic tank.The middle of the chassis frame is the core of the entire chassis frame and carries the weight of the tank, threshing drum, grain bin, cab, engine, header, trough, and battery of the rice combine harvester. Therefore, the design is mainly supported by the supporting and strengthening effect of the horizontal longitudinal beam. The front end is the load-bearing part of the cab, engine, header, trough, and partial threshing device. The force conditions are complex, so three vertical beams and three triangular beams are added in the vertical direction to strengthen the connection, and one and the lower frame connected beams are welded. The bottom frame is connected to the tracked walking system.The material of the whole frame is Q235, the thickness is 5 mm, the elastic modulusE is 196 GPa, Poisson’s ratio is 0.25, the safety factor is 1.2, the density of low-alloy steel is 7850 kg/m3, and chassis frame is obtained by Pro-E three-dimensional modeling. The frame structure is shown in Figure 6.Figure 6
Modeling diagram of the chassis frame.Chassis frame mainly plays a bearing role. The load is mainly from 8 main aspects, grain box, cab, engine, oil tank, cylinder, threshing drum, and battery. The material of the whole frame is Q235, elastic modulusE is 196 GPa, Poisson ratio μ is 0.25, safety coefficient is 1.2, and density of low-alloy steel is 7850 kg/m3. The main component variables are shown in Table 4.Mark the stress position of major components of crawler chassis, as shown in Figure7.Figure 7
Marking diagram of the force parts of the main components of the track walking chassis. (a) Grain box bearing load mark diagram. (b) Cab bearing load mark diagram. (c) Engine bearing load mark diagram. (d) Oil tank bearing load mark diagram. (e) Cylinder bearing load mark diagram. (f) Threshing drum bearing load mark diagram. (g) Battery bearing load mark diagram.
(a)
(b)
(c)
(d)
(e)
(f)
(g)


#### 2.4.2. Finite Element Analysis of Chassis Frame

In order to achieve static stress and strain analysis of the chassis frame, Finite Element modeling is required. In this paper, Pro/E is used to establish the 3D model of the chassis frame. In the 3D modeling process, in order to reduce the modeling workload and the complexity of the finite element model and improve the operation speed of the modal analysis, the model is simplified [29]. The simplified setting is based on the calculation accuracy: (1) regardless of the influence of welding on the vibration characteristics of the frame; (2) all process holes are neglected; (3) all chamfers and transition fillets are simplified to a right angle; (4) holes and small size structures in unimportant areas are ignored.The mechanical structure of the chassis frame is mainly made of square steel, rectangular steel, and connecting plates. Prior to virtual assembly, the threshing rack is divided into different submodules: the bottom crawler joint rack, the middle support chassis rack, and the upper frame rack. After drawing the parts of corresponding submodules, virtual assembly of the thresher frame is carried out from bottom to top.The built 3D model is saved in STP format, and then the material properties are defined by ANSYS 15.0 software [30]. The material selected for the chassis is Q235 steel, and its material properties are defined. The saved 3D model in STP format is imported into ANSYS Workbench, and Figure 8(a) is an import diagram of the chassis model.Figure 8
Crawler chassis frame model of ANSYS. (a) Imported chassis frame model. (b) Chassis frame bearing load mark diagram.
(a)
(b)Before the stress and strain analysis of the frame, the frame should be meshed to form a Finite Element composed of a finite number of nodes. The meshes of different sizes and shapes will have an important impact on the analysis results.Meshing platform in Finite Element Analysis software can automatically divide mesh according to the mechanical structure. The following are several partition methods offered by Meshing platform [31], Automatic (Automatic grid partition), Tetrahedrons (tetrahedral grid partition), and Hex Dominant (hexahedral grid partition). Due to the complex chassis frame structure, automatic grid division is adopted and the chassis is adjusted to a grid size of 15 mm. The gridded Finite Element Model of chassis after grid division is shown in Figure 9. After the grid division is completed, load and constraint are applied to the entity. Load is applied to each part one by one. The specific effect is shown in Figure 10.Figure 9
Meshing model of crawler chassis.Figure 10
Load distribution on the chassis frame.As shown in Figure10, A is the constraint imposed on the chassis frame; B is the oil tank load, the value is 999.6 N; C is the threshing drum load, the value is 14818N; D is the grain box load, the value is 20827N; E is cab load, the value is 3116.4 N; F is the engine load, the value is 3528N; G is the cylinder load, the value is 4226.88 N; and H is the battery load, the value is 588N; the load application direction is vertical downward. Therefore, the stress-strain diagram of the chassis frame under the low-speed full load of the rice combine harvester is obtained. The results are shown in Figure 10, which can be further based on the total variables and equivalent stresses on the obtained cloud map. The carrying capacity of each part is analyzed.


### 2.5. Crawler Chassis Performance Test

The designed crawler chassis was installed on the rice combine harvester for real vehicle test. The load-bearing chassis was simulated by high-load bearing when loading the counterweight 4 t, and the motion data under high-load pressure was collected and the chassis stability was carried out analysis. Through the spring balance method, the operating force of the joysticks designed in this paper under various conditions is measured. It is compared with the theoretical calculation value to analyze whether it conforms to the ergonomic design.


#### 2.5.1. The Driving Stability of the Bearing Test

The common running speed range of the combine harvester is 0.25 to 1.5 m/s, so the driving speed of the gearbox in the three gears is designed to be 1 m/s, 1.5 m/s, and 2 m/s. In order to verify the stability of processed crawler chassis under high load, it is necessary to test the straight speed of the harvester on the cement road surface. In addition, in order to simulate the actual movement of the harvester after bearing load, the harvester chassis is loaded on the frame by adding weight blocks until the total weight is 4t. The total length of the test is 80 m, of which the first 15 m is the acceleration and correction process of the harvester, the middle 50 m is the test data acquisition process, and the last 15 m is the deceleration and stopping process of the harvester. Three gear positions were tested separately. Five sets of tests were carried out at each gear position and the running time was recorded, which was converted into the running speed under high load. The methods of adding and weighting weight blocks to test the bearing and driving stability of the rice combine harvester are shown in Figure11.Figure 11
Counterweight block for driving stability of the rice combine harvester.


#### 2.5.2. Operating Force Test of the Operating Lever

In order to obtain the working force of the hydraulic control valve, as shown in Figure4, the resistance of the hydraulic control valve (measuring accuracy of 1g) was tested using a “Wei Heng” spring dynamometer. The test value is the mass (unit, kg), and the operating force (unit, N) is the test value multiplied by 9.81. During the test, the force of the lever should always be perpendicular to the lever. The test result is the maximum force that moves from the start point to the end point.


## 2.1. Overall Structure and Working Principle of Crawler Chassis

The crawler chassis has good field passability and overall load-bearing ability. The rice combine harvester crawler chassis is mainly made of rubber track. The crawler chassis adopts the three-layer chassis structure, which can ensure the stability of the whole machine under the condition of large load [17]. A cab is designed on the crawler chassis of the rice combine harvester, which can realize the walking and steering control of the crawler chassis. Crawler chassis can be used for walking on complicated working ground such as rice field, and various crawler rice combine harvesters can be mounted to realize field operation. Crawler chassis of rice combine harvester designed in this paper is mainly composed of three major parts: rubber track, combine harvester cab, and chassis frame. The crawler chassis structure is shown in Figure 1.Figure 1
Schematic diagram of crawler chassis of rice combine harvester.The crawler chassis of rice combine harvester is a “four wheels and one belt” structure, which is mainly composed of a driving wheel, thrust wheels, a guiding wheel, a towing wheel or a tensioning wheel, and a crawler track [18, 19]. The structure of the crawler chassis “four wheels and one belt” is shown in Figure 2.Figure 2
Structure of the “four wheels and one belt.”When the crawler chassis is walking in field, the driving wheel is rolled up from the rear by the engagement between the gear teeth on the driving wheel and the track chain under the action of the driving torque of the speed reducer. The adhesion of the track under the thrust wheel to the ground forces the drive wheel to wind up the track, and the guide pulley lays the track to ground, allowing the body to run forward along the track.


## 2.2. Design of Main Variable of Crawler Chassis

Track support lengthL, track gauge B, and track board hanging width b shall be reasonably matched to meet the requirements of grounding pressure ratio, adhesion performance, and turning performance. The initial weight of rice combine harvester is 4 t. According to the research results of reference [20], the empirical Equation for calculating crawler chassis is shown as follows:(1)L0≈1.07G3,(2)L≈L0+0.67h0,where L0 is the grounding length, the unit is m; h0 is the crawler height, the unit is m; and G is the weight of the machine, the unit is t.LetG = 4 t into equation (1) give L0 = 1700m; taking h0 as 470 mm and substituting equation (2) gives L = 1864.5 mm. The ratio of the track grounding length L0 to the gauge B is generally between 1.2 and 1.4, and the boarding width b and the grounding length L0 are generally between 0.18 and 0.22. From the abovementioned ratio relationship, B = 1307 mm and b = 340 mm.The track pitcht0 and the number of drive wheel teeth z should meet the strength and stiffness requirements. In this case, try to choose a small value to reduce the track height.According to the relationship between the pitch and the weight of the whole machine,(3)t0=15∼17.50.001G4,(4)L′≈2L0+zt02+12∼23t0+2Δ,where L′is the full length of the track, the unit is mm; T0 is track pitch, the unit is mm; and z is the number of driving wheel teeth.SubstituteG = 4 t into equation (3), then t0 = 127 mm; take z = 6, substitute t0 = 127 mm and L0 = 1700 mm into equation (4), and then L′ = 3906.1 mm.According to the research results of reference [21], the average ground pressure ratio of crawler chassis is usually 50∼58 kpa, which is an important technical variable of crawler chassis. It directly determines the passability and stability of crawler chassis structure and is also a decisive condition for the research on the adhesion torque between crawler and ground. In this paper, 50 kpa is adopted, and the track ground area is determined by the track load quality and average ground pressure, as shown in the following equation:(5)A≥G′P,(6)A=2bL0,where b is the track board hanging width, the unit is m; G′ is chassis bearing weight, the unit is N; P is the average grounding voltage ratio, the unit is pa; and A is the ground area, the unit is m2.LetG′=Gg=9.8G=39200Nbe substituted into equation (5), and bL0≥0.392 m2 can be obtained by combining the two equations (5) and (6).According to the calculated and actual data, the track hanging plate widthb is 340 mm, the grounding length L0 is 1700 mm, then the total length L′ is 3900 mm, and the full-load average grounding pressure ratio P is 33.9 kpa.The drive wheel segment circle radiusr is an important variable to calculate the performance requirements of crawler travelling devices, such as Mr and Max. The design variables of the driving wheel are mainly determined by transfer power and travel speed. When designing the belt pulley, adding the number of gears can determine the meshing tooth number when the track moves correspondingly, so as to ensure the meshing uniformity of the track and improve the overall dynamic performance. However, it also increases the overall size of the drive wheels and adds height to the chassis. Therefore, the number of driving wheel teeth z in this paper is 6. Then, the calculation equation of the drive wheel segment circle radius r is as follows:(7)D=t0sin180/z,(8)r=D2,where D is the drive wheel diameter, the unit is mm, and r is the drive wheel pitch circle radius, the unit is mm.Letz = 6 and substitute t0 = 127 mm into equation (7) to get D = 254 mm. Then, substitute into equation (8) to get r = 127 mm.


## 2.3. Development and Design of Rice Combine Harvester Cab

The cab of crawler chassis is mainly composed of a driving seat, a central bedplate, a side control panel, and various joysticks. The crawler chassis of track designed in this paper is shown in Figure3. From the Chinese adult male body size and sitting size, the size, stroke, and steering angle of the operating levers are reasonably designed. Based on the ergonomics theory, the relative position of the joystick suitable for the majority of Chinese adult male operators was designed, and the layout optimization analysis of human-machine control interface cab was carried out [22, 23].Figure 3
Top view of the combine harvester cab.


### 2.3.1. Design of Operating Lever

The operating levers of the rice combine harvester are divided into two categories according to their structure and principle, small switch stroke, and large switch stroke. The small switch stroke is like the reel lever and the header control lever [24]. The structure of the lever and the principle of simplified operating lever are shown in Figure 4.Figure 4
Small switch travel of the reel and principles of the operating lever.By querying the relevant variable of the existing valve body, it can be known that the stroke required for the valve body switch connected with the unloading clutch lever, reel operating lever, and brake lever is 10 mm, and the stroke of the valve body switch connected to the forward and backward operating lever is 20 mm. The valve body switch connected to the shift lever is required to have a stroke of plus or minus 35 mm, the stroke of the valve body switch connected to the cutting table integrated joystick is 20 mm, and the stroke of the valve body switch connected to the harvesting device joystick is 80 mm.Structure of the rod shown in left part of Figure4 is simplified to the linkage mechanism shown in right part of Figure 4. Through the analysis of the model, the required manipulation angle of the rod member when the corresponding valve body switch is completed can be obtained. Manipulate the amount of displacement.Set the length of theCD rod up and down displacement DD', that is, the switch stroke is c, and set the rotation angle of the rod during the work is θ, BC = l2, CD = l3, ∠ABA′＝∠CBC′ = θ, where θ is the designed.In ΔCBC', the triangle is an isosceles triangle, where BC=BC',(9)HD′=l3−l2sinθ+c,2l22cosθ+2l2l3+csinθ=2l22+c2+2l3c.According to the weight value and priority of the human-machine interface of the rice combine harvester, we should pay more attention to the design of the joystick in the cab. According to relevant studies [25], priority sequence and weight values of main joystick parts in each cab are shown in Table 1. We can conduct comparative analysis on the rationality of theoretical design of the joystick based on the priority of joystick.Table 1
Weight value and priority of each component of human-machine interface of combine harvester cab.
No.
The evaluation object
Frequency of utilization %
Priority order
1
Unloading clutch operating lever
3
4
Reel operating lever
2
Forward and backward operating lever
80
1
3
Shift lever
5
3
4
Cutting table integrated joystick
10
2
5
Harvesting device joystick
1
5
6
Brake lever
1
6In order to analyze and design the operating force of operating levers later, the switch strokec of the bar members and the length l2 and l3 of the operating levers can be obtained from the previous paragraph. By putting them into equation (9), the rotation angle θ of the main operating levers in the cab can be calculated.In the case of designingl2, l3, θ, and other variable of each lever, the length of the hand holding part of each lever is set according to the simplified mechanical analysis of the operation process of the joystick and the optimal operation force of the hand. Relevant studies show that the minimum operating force of the back of the human hand is 10N, and if the operating force of the hand is less than 10 N, the controllability is not good. The maximum front and rear operating force of the hand is 130 N, and when the operating force is greater than 130 N, the controllability exceeds the 95th percentile adult male hand operating force in China. According to the research results of reference [26], the optimal average arm operating force of Chinese adults is 40N, the maximum left-right operating force of a handle is 90 N, and the optimal average arm operating force from left to right is 30 N. Based on the following mechanical analysis, we complete the design of various joystick lengths.Since the operation process is a variable force process, in order to simplify the calculation, the calculation is performed at two moments when the joystick is moved to the intermediate position and the final position. The direction of the operating force is always perpendicular to the rod, and the position at every moment between the movements to the final state is simplified to the equilibrium state. The frictional resistancef only exists in uniform rod BC, and take f for 80 N. Let rotation angle be θ, operating force F1, the bottom connection body bar stress F2, the length of lever AB l1, the length of lever BC l2, the length of lever CD l3, the switch travel movement GD c, and the length of lever BJ l4. Let ∠BC'J = θ1, ∠BCC' = θ2, ∠CD'C' = θ3, and ∠CC'D = θ4. Among them operating force F1 of each operating lever is desired.According to Figure4, it can be known from the moment balance that(10)F1⋅l1=F2⋅l4+f⋅l2.From the isosceles triangle BCC', we know that(11)∠BC′C=∠BCC′=θ2=180−θ2,θ4=θ2.In the triangle CDF, according to the law of cosines, we can know that(12)θ3=arccos2l32+c2+2l3⋅c−4l22sin2θ/22l32+2l3⋅c.In the triangleBC'J, l4=l2⋅sinθ1.From equations (10) and (12), we can obtain(13)F1=F2⋅l4l1+f⋅l2l1=F2⋅l2⋅sin180−θ/2−arccos2l32+c2+2l3⋅c−4l22sin2θ/2/2l32+2l3⋅c+θ/2+f⋅l2l1.The componentF3 of F2 in the vertical direction is the force required to open the valve body, so F3=F2 cosθ3. The magnitude of this value varies according to the valve body. The relevant data can be seen that the required force F3 of the switch valve body is 40 N. Thereby, the specific value of each joystick F2 can be calculated, and the design value of the length l1 of the joystick is finally completed. The results of the overall joystick design are shown in Table 2.Table 2
Main dimensions of Chinese adult male human body (mm).
No.
Percentile
Height
Weight
Upper arm length
Forearm length
Thigh length
Shank length
1
5
1583
48
289
216
428
338
2
50
1678
59
313
237
465
369
3
95
1775
75
338
258
505
403


### 2.3.2. Cab Maneuvering Space Layout

Since most of the combine harvester operators are male, the overall design of the cab is based on the body size of Chinese adult males, but the design method of this paper is also applicable to the cab of female operators. Chinese adult body size is the main source of design data and size reference for this design [27]. The main dimensions of male human body in the 5th, 50th, and 95th percentiles of Chinese adult human body are shown in Table 2, and the sitting variable of the male human body in the 5th, 50th, and 95th percentiles of Chinese adult human body are shown in Table 3.Table 3
Sitting variable of Chinese adult male human body (mm).
No
Percentile
Sitting height
Sitting position cervical high point
Sitting eye height
Sitting shoulder high
Sitting cubits high
Sitting thigh thick
Sitting knee height
Leg to foot height
Hip and knee distance
Sitting leg length
1
5
858
615
749
557
228
112
456
383
515
921
2
50
908
657
798
598
263
130
493
413
554
992
3
95
947
691
836
631
291
146
523
439
585
1046In the actual design calculation, due to the influence of the workers’ clothing, shoes, posture, and psychological factors, it is necessary to add an appropriate amount of correction to the design. The shoe wear correction amount is increased by 25 mm based on the measured value, and the dressing correction amount is increased, such as the hip width, by 15 mm on the basis of the measurement. In the actual situation, the operator mostly operates in a relaxed state, so a certain amount of correction should be subtracted from the standard of standing height and eye height.According to the principle of ergonomics, the range of the upper limbs determines the range of the working space in the sitting position. Also, the comfortable working range changes with the height of the working surface, the distance of the hand from the center line of the human body, and the height of the hand. In addition, the range will be affected by the dress. Tables2 and 3 can be designed, as shown in Figure 5, for the 95th percentile adult upper limb horizontal working area in China. The design of the combine harvester cab has a design space of 1400 × 1100 × 1350 cuboid.Figure 5
Low-speed full-load stress-strain diagram. (a) Equivalent stress diagram at low speed and full load. (b) Strain distribution at low speed and full load.
(a)
(b)


## 2.3.1. Design of Operating Lever

The operating levers of the rice combine harvester are divided into two categories according to their structure and principle, small switch stroke, and large switch stroke. The small switch stroke is like the reel lever and the header control lever [24]. The structure of the lever and the principle of simplified operating lever are shown in Figure 4.Figure 4
Small switch travel of the reel and principles of the operating lever.By querying the relevant variable of the existing valve body, it can be known that the stroke required for the valve body switch connected with the unloading clutch lever, reel operating lever, and brake lever is 10 mm, and the stroke of the valve body switch connected to the forward and backward operating lever is 20 mm. The valve body switch connected to the shift lever is required to have a stroke of plus or minus 35 mm, the stroke of the valve body switch connected to the cutting table integrated joystick is 20 mm, and the stroke of the valve body switch connected to the harvesting device joystick is 80 mm.Structure of the rod shown in left part of Figure4 is simplified to the linkage mechanism shown in right part of Figure 4. Through the analysis of the model, the required manipulation angle of the rod member when the corresponding valve body switch is completed can be obtained. Manipulate the amount of displacement.Set the length of theCD rod up and down displacement DD', that is, the switch stroke is c, and set the rotation angle of the rod during the work is θ, BC = l2, CD = l3, ∠ABA′＝∠CBC′ = θ, where θ is the designed.In ΔCBC', the triangle is an isosceles triangle, where BC=BC',(9)HD′=l3−l2sinθ+c,2l22cosθ+2l2l3+csinθ=2l22+c2+2l3c.According to the weight value and priority of the human-machine interface of the rice combine harvester, we should pay more attention to the design of the joystick in the cab. According to relevant studies [25], priority sequence and weight values of main joystick parts in each cab are shown in Table 1. We can conduct comparative analysis on the rationality of theoretical design of the joystick based on the priority of joystick.Table 1
Weight value and priority of each component of human-machine interface of combine harvester cab.
No.
The evaluation object
Frequency of utilization %
Priority order
1
Unloading clutch operating lever
3
4
Reel operating lever
2
Forward and backward operating lever
80
1
3
Shift lever
5
3
4
Cutting table integrated joystick
10
2
5
Harvesting device joystick
1
5
6
Brake lever
1
6In order to analyze and design the operating force of operating levers later, the switch strokec of the bar members and the length l2 and l3 of the operating levers can be obtained from the previous paragraph. By putting them into equation (9), the rotation angle θ of the main operating levers in the cab can be calculated.In the case of designingl2, l3, θ, and other variable of each lever, the length of the hand holding part of each lever is set according to the simplified mechanical analysis of the operation process of the joystick and the optimal operation force of the hand. Relevant studies show that the minimum operating force of the back of the human hand is 10N, and if the operating force of the hand is less than 10 N, the controllability is not good. The maximum front and rear operating force of the hand is 130 N, and when the operating force is greater than 130 N, the controllability exceeds the 95th percentile adult male hand operating force in China. According to the research results of reference [26], the optimal average arm operating force of Chinese adults is 40N, the maximum left-right operating force of a handle is 90 N, and the optimal average arm operating force from left to right is 30 N. Based on the following mechanical analysis, we complete the design of various joystick lengths.Since the operation process is a variable force process, in order to simplify the calculation, the calculation is performed at two moments when the joystick is moved to the intermediate position and the final position. The direction of the operating force is always perpendicular to the rod, and the position at every moment between the movements to the final state is simplified to the equilibrium state. The frictional resistancef only exists in uniform rod BC, and take f for 80 N. Let rotation angle be θ, operating force F1, the bottom connection body bar stress F2, the length of lever AB l1, the length of lever BC l2, the length of lever CD l3, the switch travel movement GD c, and the length of lever BJ l4. Let ∠BC'J = θ1, ∠BCC' = θ2, ∠CD'C' = θ3, and ∠CC'D = θ4. Among them operating force F1 of each operating lever is desired.According to Figure4, it can be known from the moment balance that(10)F1⋅l1=F2⋅l4+f⋅l2.From the isosceles triangle BCC', we know that(11)∠BC′C=∠BCC′=θ2=180−θ2,θ4=θ2.In the triangle CDF, according to the law of cosines, we can know that(12)θ3=arccos2l32+c2+2l3⋅c−4l22sin2θ/22l32+2l3⋅c.In the triangleBC'J, l4=l2⋅sinθ1.From equations (10) and (12), we can obtain(13)F1=F2⋅l4l1+f⋅l2l1=F2⋅l2⋅sin180−θ/2−arccos2l32+c2+2l3⋅c−4l22sin2θ/2/2l32+2l3⋅c+θ/2+f⋅l2l1.The componentF3 of F2 in the vertical direction is the force required to open the valve body, so F3=F2 cosθ3. The magnitude of this value varies according to the valve body. The relevant data can be seen that the required force F3 of the switch valve body is 40 N. Thereby, the specific value of each joystick F2 can be calculated, and the design value of the length l1 of the joystick is finally completed. The results of the overall joystick design are shown in Table 2.Table 2
Main dimensions of Chinese adult male human body (mm).
No.
Percentile
Height
Weight
Upper arm length
Forearm length
Thigh length
Shank length
1
5
1583
48
289
216
428
338
2
50
1678
59
313
237
465
369
3
95
1775
75
338
258
505
403


## 2.3.2. Cab Maneuvering Space Layout

Since most of the combine harvester operators are male, the overall design of the cab is based on the body size of Chinese adult males, but the design method of this paper is also applicable to the cab of female operators. Chinese adult body size is the main source of design data and size reference for this design [27]. The main dimensions of male human body in the 5th, 50th, and 95th percentiles of Chinese adult human body are shown in Table 2, and the sitting variable of the male human body in the 5th, 50th, and 95th percentiles of Chinese adult human body are shown in Table 3.Table 3
Sitting variable of Chinese adult male human body (mm).
No
Percentile
Sitting height
Sitting position cervical high point
Sitting eye height
Sitting shoulder high
Sitting cubits high
Sitting thigh thick
Sitting knee height
Leg to foot height
Hip and knee distance
Sitting leg length
1
5
858
615
749
557
228
112
456
383
515
921
2
50
908
657
798
598
263
130
493
413
554
992
3
95
947
691
836
631
291
146
523
439
585
1046In the actual design calculation, due to the influence of the workers’ clothing, shoes, posture, and psychological factors, it is necessary to add an appropriate amount of correction to the design. The shoe wear correction amount is increased by 25 mm based on the measured value, and the dressing correction amount is increased, such as the hip width, by 15 mm on the basis of the measurement. In the actual situation, the operator mostly operates in a relaxed state, so a certain amount of correction should be subtracted from the standard of standing height and eye height.According to the principle of ergonomics, the range of the upper limbs determines the range of the working space in the sitting position. Also, the comfortable working range changes with the height of the working surface, the distance of the hand from the center line of the human body, and the height of the hand. In addition, the range will be affected by the dress. Tables2 and 3 can be designed, as shown in Figure 5, for the 95th percentile adult upper limb horizontal working area in China. The design of the combine harvester cab has a design space of 1400 × 1100 × 1350 cuboid.Figure 5
Low-speed full-load stress-strain diagram. (a) Equivalent stress diagram at low speed and full load. (b) Strain distribution at low speed and full load.
(a)
(b)


## 2.4. Chassis Frame Design

### 2.4.1. Chassis Frame Structure and Bearing Variables

The chassis frame consists of four main beams, five main longitudinal beams, and auxiliary beams supporting other components, which are placed at the fulcrum of the main load such as the grain bin, threshing drum, engine, and bridge [28]. The chassis frame is made of 30 × 30 mm, 40 × 40 mm, and 40 × 60 mm square tubes and rectangular tubes of different specifications. The thickness of the chassis is 2 mm, 3 mm, 4 mm, and 6 mm, and the connecting plate is used for fixing and strengthening. The entire rack is 3.807 m long, 2.163 m wide, and 1.036 m high.The chassis frame adopts a 3-layer structure. The upper layer mainly carries the weight of the cab. The frame structure is used to increase the contact area with the cab so that the force is even, the stress and strain of the frame are reduced, and the bearing performance is improved. The frame is used for placing the hydraulic tank.The middle of the chassis frame is the core of the entire chassis frame and carries the weight of the tank, threshing drum, grain bin, cab, engine, header, trough, and battery of the rice combine harvester. Therefore, the design is mainly supported by the supporting and strengthening effect of the horizontal longitudinal beam. The front end is the load-bearing part of the cab, engine, header, trough, and partial threshing device. The force conditions are complex, so three vertical beams and three triangular beams are added in the vertical direction to strengthen the connection, and one and the lower frame connected beams are welded. The bottom frame is connected to the tracked walking system.The material of the whole frame is Q235, the thickness is 5 mm, the elastic modulusE is 196 GPa, Poisson’s ratio is 0.25, the safety factor is 1.2, the density of low-alloy steel is 7850 kg/m3, and chassis frame is obtained by Pro-E three-dimensional modeling. The frame structure is shown in Figure 6.Figure 6
Modeling diagram of the chassis frame.Chassis frame mainly plays a bearing role. The load is mainly from 8 main aspects, grain box, cab, engine, oil tank, cylinder, threshing drum, and battery. The material of the whole frame is Q235, elastic modulusE is 196 GPa, Poisson ratio μ is 0.25, safety coefficient is 1.2, and density of low-alloy steel is 7850 kg/m3. The main component variables are shown in Table 4.Mark the stress position of major components of crawler chassis, as shown in Figure7.Figure 7
Marking diagram of the force parts of the main components of the track walking chassis. (a) Grain box bearing load mark diagram. (b) Cab bearing load mark diagram. (c) Engine bearing load mark diagram. (d) Oil tank bearing load mark diagram. (e) Cylinder bearing load mark diagram. (f) Threshing drum bearing load mark diagram. (g) Battery bearing load mark diagram.
(a)
(b)
(c)
(d)
(e)
(f)
(g)


### 2.4.2. Finite Element Analysis of Chassis Frame

In order to achieve static stress and strain analysis of the chassis frame, Finite Element modeling is required. In this paper, Pro/E is used to establish the 3D model of the chassis frame. In the 3D modeling process, in order to reduce the modeling workload and the complexity of the finite element model and improve the operation speed of the modal analysis, the model is simplified [29]. The simplified setting is based on the calculation accuracy: (1) regardless of the influence of welding on the vibration characteristics of the frame; (2) all process holes are neglected; (3) all chamfers and transition fillets are simplified to a right angle; (4) holes and small size structures in unimportant areas are ignored.The mechanical structure of the chassis frame is mainly made of square steel, rectangular steel, and connecting plates. Prior to virtual assembly, the threshing rack is divided into different submodules: the bottom crawler joint rack, the middle support chassis rack, and the upper frame rack. After drawing the parts of corresponding submodules, virtual assembly of the thresher frame is carried out from bottom to top.The built 3D model is saved in STP format, and then the material properties are defined by ANSYS 15.0 software [30]. The material selected for the chassis is Q235 steel, and its material properties are defined. The saved 3D model in STP format is imported into ANSYS Workbench, and Figure 8(a) is an import diagram of the chassis model.Figure 8
Crawler chassis frame model of ANSYS. (a) Imported chassis frame model. (b) Chassis frame bearing load mark diagram.
(a)
(b)Before the stress and strain analysis of the frame, the frame should be meshed to form a Finite Element composed of a finite number of nodes. The meshes of different sizes and shapes will have an important impact on the analysis results.Meshing platform in Finite Element Analysis software can automatically divide mesh according to the mechanical structure. The following are several partition methods offered by Meshing platform [31], Automatic (Automatic grid partition), Tetrahedrons (tetrahedral grid partition), and Hex Dominant (hexahedral grid partition). Due to the complex chassis frame structure, automatic grid division is adopted and the chassis is adjusted to a grid size of 15 mm. The gridded Finite Element Model of chassis after grid division is shown in Figure 9. After the grid division is completed, load and constraint are applied to the entity. Load is applied to each part one by one. The specific effect is shown in Figure 10.Figure 9
Meshing model of crawler chassis.Figure 10
Load distribution on the chassis frame.As shown in Figure10, A is the constraint imposed on the chassis frame; B is the oil tank load, the value is 999.6 N; C is the threshing drum load, the value is 14818N; D is the grain box load, the value is 20827N; E is cab load, the value is 3116.4 N; F is the engine load, the value is 3528N; G is the cylinder load, the value is 4226.88 N; and H is the battery load, the value is 588N; the load application direction is vertical downward. Therefore, the stress-strain diagram of the chassis frame under the low-speed full load of the rice combine harvester is obtained. The results are shown in Figure 10, which can be further based on the total variables and equivalent stresses on the obtained cloud map. The carrying capacity of each part is analyzed.


## 2.4.1. Chassis Frame Structure and Bearing Variables

The chassis frame consists of four main beams, five main longitudinal beams, and auxiliary beams supporting other components, which are placed at the fulcrum of the main load such as the grain bin, threshing drum, engine, and bridge [28]. The chassis frame is made of 30 × 30 mm, 40 × 40 mm, and 40 × 60 mm square tubes and rectangular tubes of different specifications. The thickness of the chassis is 2 mm, 3 mm, 4 mm, and 6 mm, and the connecting plate is used for fixing and strengthening. The entire rack is 3.807 m long, 2.163 m wide, and 1.036 m high.The chassis frame adopts a 3-layer structure. The upper layer mainly carries the weight of the cab. The frame structure is used to increase the contact area with the cab so that the force is even, the stress and strain of the frame are reduced, and the bearing performance is improved. The frame is used for placing the hydraulic tank.The middle of the chassis frame is the core of the entire chassis frame and carries the weight of the tank, threshing drum, grain bin, cab, engine, header, trough, and battery of the rice combine harvester. Therefore, the design is mainly supported by the supporting and strengthening effect of the horizontal longitudinal beam. The front end is the load-bearing part of the cab, engine, header, trough, and partial threshing device. The force conditions are complex, so three vertical beams and three triangular beams are added in the vertical direction to strengthen the connection, and one and the lower frame connected beams are welded. The bottom frame is connected to the tracked walking system.The material of the whole frame is Q235, the thickness is 5 mm, the elastic modulusE is 196 GPa, Poisson’s ratio is 0.25, the safety factor is 1.2, the density of low-alloy steel is 7850 kg/m3, and chassis frame is obtained by Pro-E three-dimensional modeling. The frame structure is shown in Figure 6.Figure 6
Modeling diagram of the chassis frame.Chassis frame mainly plays a bearing role. The load is mainly from 8 main aspects, grain box, cab, engine, oil tank, cylinder, threshing drum, and battery. The material of the whole frame is Q235, elastic modulusE is 196 GPa, Poisson ratio μ is 0.25, safety coefficient is 1.2, and density of low-alloy steel is 7850 kg/m3. The main component variables are shown in Table 4.Mark the stress position of major components of crawler chassis, as shown in Figure7.Figure 7
Marking diagram of the force parts of the main components of the track walking chassis. (a) Grain box bearing load mark diagram. (b) Cab bearing load mark diagram. (c) Engine bearing load mark diagram. (d) Oil tank bearing load mark diagram. (e) Cylinder bearing load mark diagram. (f) Threshing drum bearing load mark diagram. (g) Battery bearing load mark diagram.
(a)
(b)
(c)
(d)
(e)
(f)
(g)


## 2.4.2. Finite Element Analysis of Chassis Frame

In order to achieve static stress and strain analysis of the chassis frame, Finite Element modeling is required. In this paper, Pro/E is used to establish the 3D model of the chassis frame. In the 3D modeling process, in order to reduce the modeling workload and the complexity of the finite element model and improve the operation speed of the modal analysis, the model is simplified [29]. The simplified setting is based on the calculation accuracy: (1) regardless of the influence of welding on the vibration characteristics of the frame; (2) all process holes are neglected; (3) all chamfers and transition fillets are simplified to a right angle; (4) holes and small size structures in unimportant areas are ignored.The mechanical structure of the chassis frame is mainly made of square steel, rectangular steel, and connecting plates. Prior to virtual assembly, the threshing rack is divided into different submodules: the bottom crawler joint rack, the middle support chassis rack, and the upper frame rack. After drawing the parts of corresponding submodules, virtual assembly of the thresher frame is carried out from bottom to top.The built 3D model is saved in STP format, and then the material properties are defined by ANSYS 15.0 software [30]. The material selected for the chassis is Q235 steel, and its material properties are defined. The saved 3D model in STP format is imported into ANSYS Workbench, and Figure 8(a) is an import diagram of the chassis model.Figure 8
Crawler chassis frame model of ANSYS. (a) Imported chassis frame model. (b) Chassis frame bearing load mark diagram.
(a)
(b)Before the stress and strain analysis of the frame, the frame should be meshed to form a Finite Element composed of a finite number of nodes. The meshes of different sizes and shapes will have an important impact on the analysis results.Meshing platform in Finite Element Analysis software can automatically divide mesh according to the mechanical structure. The following are several partition methods offered by Meshing platform [31], Automatic (Automatic grid partition), Tetrahedrons (tetrahedral grid partition), and Hex Dominant (hexahedral grid partition). Due to the complex chassis frame structure, automatic grid division is adopted and the chassis is adjusted to a grid size of 15 mm. The gridded Finite Element Model of chassis after grid division is shown in Figure 9. After the grid division is completed, load and constraint are applied to the entity. Load is applied to each part one by one. The specific effect is shown in Figure 10.Figure 9
Meshing model of crawler chassis.Figure 10
Load distribution on the chassis frame.As shown in Figure10, A is the constraint imposed on the chassis frame; B is the oil tank load, the value is 999.6 N; C is the threshing drum load, the value is 14818N; D is the grain box load, the value is 20827N; E is cab load, the value is 3116.4 N; F is the engine load, the value is 3528N; G is the cylinder load, the value is 4226.88 N; and H is the battery load, the value is 588N; the load application direction is vertical downward. Therefore, the stress-strain diagram of the chassis frame under the low-speed full load of the rice combine harvester is obtained. The results are shown in Figure 10, which can be further based on the total variables and equivalent stresses on the obtained cloud map. The carrying capacity of each part is analyzed.


## 2.5. Crawler Chassis Performance Test

The designed crawler chassis was installed on the rice combine harvester for real vehicle test. The load-bearing chassis was simulated by high-load bearing when loading the counterweight 4 t, and the motion data under high-load pressure was collected and the chassis stability was carried out analysis. Through the spring balance method, the operating force of the joysticks designed in this paper under various conditions is measured. It is compared with the theoretical calculation value to analyze whether it conforms to the ergonomic design.


### 2.5.1. The Driving Stability of the Bearing Test

The common running speed range of the combine harvester is 0.25 to 1.5 m/s, so the driving speed of the gearbox in the three gears is designed to be 1 m/s, 1.5 m/s, and 2 m/s. In order to verify the stability of processed crawler chassis under high load, it is necessary to test the straight speed of the harvester on the cement road surface. In addition, in order to simulate the actual movement of the harvester after bearing load, the harvester chassis is loaded on the frame by adding weight blocks until the total weight is 4t. The total length of the test is 80 m, of which the first 15 m is the acceleration and correction process of the harvester, the middle 50 m is the test data acquisition process, and the last 15 m is the deceleration and stopping process of the harvester. Three gear positions were tested separately. Five sets of tests were carried out at each gear position and the running time was recorded, which was converted into the running speed under high load. The methods of adding and weighting weight blocks to test the bearing and driving stability of the rice combine harvester are shown in Figure11.Figure 11
Counterweight block for driving stability of the rice combine harvester.


### 2.5.2. Operating Force Test of the Operating Lever

In order to obtain the working force of the hydraulic control valve, as shown in Figure4, the resistance of the hydraulic control valve (measuring accuracy of 1g) was tested using a “Wei Heng” spring dynamometer. The test value is the mass (unit, kg), and the operating force (unit, N) is the test value multiplied by 9.81. During the test, the force of the lever should always be perpendicular to the lever. The test result is the maximum force that moves from the start point to the end point.


## 2.5.1. The Driving Stability of the Bearing Test

The common running speed range of the combine harvester is 0.25 to 1.5 m/s, so the driving speed of the gearbox in the three gears is designed to be 1 m/s, 1.5 m/s, and 2 m/s. In order to verify the stability of processed crawler chassis under high load, it is necessary to test the straight speed of the harvester on the cement road surface. In addition, in order to simulate the actual movement of the harvester after bearing load, the harvester chassis is loaded on the frame by adding weight blocks until the total weight is 4t. The total length of the test is 80 m, of which the first 15 m is the acceleration and correction process of the harvester, the middle 50 m is the test data acquisition process, and the last 15 m is the deceleration and stopping process of the harvester. Three gear positions were tested separately. Five sets of tests were carried out at each gear position and the running time was recorded, which was converted into the running speed under high load. The methods of adding and weighting weight blocks to test the bearing and driving stability of the rice combine harvester are shown in Figure11.Figure 11
Counterweight block for driving stability of the rice combine harvester.


## 2.5.2. Operating Force Test of the Operating Lever

In order to obtain the working force of the hydraulic control valve, as shown in Figure4, the resistance of the hydraulic control valve (measuring accuracy of 1g) was tested using a “Wei Heng” spring dynamometer. The test value is the mass (unit, kg), and the operating force (unit, N) is the test value multiplied by 9.81. During the test, the force of the lever should always be perpendicular to the lever. The test result is the maximum force that moves from the start point to the end point.


## 3. Results and Discussion

### 3.1. Cab Variable Design of Crawler Chassis

#### 3.1.1. Results of Operating Levers Variable Design

The connecting rod variable of unloading clutch operating lever and the reel operating lever arel2 = 75 mm and l3 = 400 mm, c = 10 mm is brought into equation (9), the rotation angle θ1 = 7.66° can be obtained, and the displacement of the rod is 55 mm. The connecting rod variable of the forward and backward operating lever are l2 = 45 mm and l3 = 270 mm, c = 20 mm with the input equation (9), the rotation angle θ2 = 26.44° can be obtained, and the displacement of the rod is 182 mm; shift lever’s variable l2 = 180 mm and l3 = 680 mm, c = 70 mm is brought in equation (9), the rotation angle θ3 = 22.94° can be obtained, and the rod displacement is 155 mm. The connecting rod variables of the cutting table integrated joystick l2 = 65 mm and l3 = 410 mm, c = 20 mm is brought in equation (9), the rotation angle θ4 = 17.9° can be obtained, and the displacement of the rod is 148 mm. The connecting rod variables of the harvesting device joystick l2 = 95 mm and l3 = 480 mm, c = 40 mm is brought in equation (9), the rotation angle θ5 = 24.95° can be obtained, and the displacement of the rod is 78 mm; the connecting rod variable of the brake joystick is l2 = 50 mm and l3 = 400 mm, c = 10 mm is brought in equation (9), the rotation angle θ6 = 11.53° can be obtained, and the displacement of the rod is 55 mm.The BC rod lengthl2, the CD rod length l3, the switch stroke c, the rotation angle θ, and the theoretical operating force F are substituted into equation (13) to obtain the length l1 of each rod handle, and the working variable of each rod are shown in – 4.Table 4
Design variable and theoretical operating force of the joystick.
No.
The evaluation object
Length of AB 11/mm
Length of BC l2/mm
Length of CD l3/mm
Switch strokec (mm)
Rotation angleθ/°
Displacement of the rod /mm
Theoretical operating forceF/N 1Unloading clutch operating lever reel operating lever28075400107.665532.02Forward and backward operating lever450452702026.4218211.553Shift lever4201806807020.0015443.934Cutting table integrated joystick350654102023.2114821.915Harvesting device joystick280954804018.247839.346Brake lever220504001011.545527.8


#### 3.1.2. Chinese Adult Male Upper Limb Level Work Area Design

According to the data and analysis in Tables2 and 3, the 95th percentile upper limb horizontal operation area in China is obtained, as shown in Figure 12.Figure 12
Schematic diagram of horizontal working area of man’s upper limbs.As shown in Figure12, area I is a comfortable manipulation area, the range of which is the envelope area with the shoulder joint as the center and R400 as the radius. Area III is the effective operation area, which is equivalent to the range of upper limb function. Area IV is an expandable operation area, which is defined as the area that can be properly changed (inclined and bent) and the hand can be reached in the correct sitting position. Joystick location layout should meet within the scope of regional III. Surface height should be able to make the person’s upper arms naturally prolapse, which is in a state of relaxed and comfortable. Arm should be as far as possible under level or slightly oblique. This will reduce arm soreness. Based on the abovementioned analysis, an ideal relative position of the bars can be obtained, so as to design the overall space layout of the cab.


#### 3.1.3. Design of Cab Maneuvering Space Layout

Combining the data in Tables2 and 3 with the corrections, the sum of the elbow height and the calf plus foot height of the lower man in the 50th percentile sitting position is 676 mm. Taking into account the amount of shoe and dressing correction (40 mm), the vertical distance between the elbow and foot of the 50th percentile man is 716 mm, and the height of the working surface is 500 mm, which is the height of the console. The best height is 178–203 mm above the H point (H point is the span point), and the vertical height of the lever handle position should be designed to be 100–250 mm higher than the console. Therefore, the designed reel operating lever is 160 mm higher than the console. The forward and backward operating lever is 250 mm higher than the console. The shift lever is 200 mm above the console. The brake lever is 100 mm higher than the console.According to the calculated steering angle of each lever and the specified height of levers higher than the console, the length of the lever stroke groove of the console can be determined. Through calculation, the slot length of the reel operating lever on the console is 40 mm (the data are rounded and the functional stroke is 33 mm). The upper end of the reel operating lever groove makes the reel lower, and the lower end raises the reel. The groove of cutting table integrated joystick is Mi-shaped. In order to simplify the processing, we design the groove to be a circle with a diameter of 85 mm. The left end of the groove turns the harvester left and the right end turns the harvester right, and the upper end makes the header and the lower end raises the header. The length of the forward and backward operating lever groove is 120 mm (bidirectional, stepped, and the functional stroke is 92 mm), the front section of the groove advances the harvester, the middle of the groove stops the harvester, and the rear end of the groove moves the harvester backward. The length of the shift lever groove on the console is 180 mm (the function stroke is 150 mm); the front section of the groove represents the standard speed, and the rear end of the groove represents low speed. The length of the brake lever groove is 145 mm, and the front section of the groove represents the state of small throttle; the rear end of the groove represents the state of large throttle.The control console in the cab is mainly composed of a side control panel, which is located on the left-hand side of the driver. The central bedplate is located directly in front of the driver. Therefore, the length, width, and thickness of the instrument panel of the central control console are 1100 mm, 180 mm, and 2 mm, respectively. The length, width, and thickness of the instrument panel of the measurement and control console are 1200 mm, 310 mm, and 2 mm, respectively. After manufacturing the grooves required for the instrument panel and levers, distribute the levers in the normal working area of the driver’s left and right hands. Taking the left and right shoulders of the driver as the center of the circle, the radius of 400 mm is the most suitable area for the distribution of the rods. The rods should not exceed the radius of a circle with the shoulder as the center and a radius of 550 mm. The overall space layout of the designed cab and the internal structure of the bar are shown in Figures13 and 14 below.Figure 13
Overall layout model of cab maneuvering space.Figure 14
Internal structure of the operating lever.


#### 3.1.4. Stress and Strain Analysis of the Chassis Frame

The static analysis is mainly used to analyze the deformation and equivalent stress of the chassis after being loaded. According to the value of the total variables and the equivalent stress on the cloud map, the bearing capacity of each part of the chassis is analyzed [32]. Based on the previous meshing, loading and restraining of the chassis frame, the stress-strain cloud map is obtained as Figure 5.According to Figure5(a), it can be seen that the distribution of large stress is concentrated at the connection between the upper frame and the middle frame, the horizontal resistance of the crawler to the frame and the compression part of the grain box. So, the maximum stress is less than 173.25 Mpa. There is no stress concentration. The yield strength of Q235 material is 235 Mpa, which is meeting the requirements of Q235. According to Figure 5(b), the most serious deformation of the chassis frame is the red part, which is about 9.2504 mm. Because of full load, the bearing part of the grain box is the largest pressure. The supporting beam of the load-bearing part is a cantilever beam structure, where the bending moment is large and the deformation is the most obvious. The second largest part of the deformation is the fuel tank, and the deformation is 1.0278 to 5.1391 mm. This is because the fuel tank is at the farthest edge of the frame, and there is not enough support beams in the longitudinal direction to share the load. The third largest part of the deformation is the cab, and the total deformation is 0 to 5.1391 mm. This is because the entire bridge support is also in a suspended state, with insufficient support, resulting in a relatively large deformation. So, when the total weight is about 4 t in full load, the maximum shape variable is 9.2504 mm. The strength and stiffness of the chassis frame meet the design requirements.


### 3.2. Physical Assembly and Production

#### 3.2.1. Integral Assembly of Mechanical Model

From the perspective of the overall configuration of the whole machine, the cab is placed above the frame of crawler on the right side of the crawler chassis. The space adjustment of each solid module is carried out to ensure reasonable space configuration and balanced center of gravity configuration of the whole machine. The integral assembly of crawler chassis is shown in Figure15.Figure 15
Integral assembly of crawler chassis.


#### 3.2.2. Production of Test Prototype

According to the variable shown in Tables2, 3, and 5, each device was developed and manufactured in Dongfeng agricultural machine Co., Ltd. The chassis frame is welded with square and rectangular pipes of different specifications such as 30 × 30 mm, 40 × 40 mm, and 40 × 60 mm. The chassis frame is 3.807 m long, 2.163 m wide, and 1.036 m high. The suspension plate width of the rubber track is 340 mm. The grounding length is 1700 mm. The total length is 3900 mm. The full-load average grounding pressure ratio is 33.9 kpa. The size of the cab is 1400 × 1100 × 1350 mm, which is placed above the track on the right side of the chassis frame to complete the overall assembly. The actual picture of crawler chassis of rice combine harvester is shown in Figure 16.Table 5
Main component variable of the combine harvester.
Main load
Grain box
Cab
Engine
Oil tank
Cylinder
Threshing drum
Battery
Working weight (kg)
1771
265
300
85
359.4
1260
50
Bearing area (m2)
0.0560
0.1760
0.0264
0.1350
0.0142
0.1585
0.0154
Intensity of full-load pressure (MPa)
0.3098
0.0150
0.1040
0.0617
0.2480
0.0779
0.0319
Allowable load (N)
20826.9 6
3116.4
3528
999.6
4226.88
14817.6
588Figure 16
Production of crawler chassis of the combine harvester.


### 3.3. Comparative Analysis of Theoretical Design and Experimental Results

#### 3.3.1. Joystick Design and Control Force Test

The operating force of the operating lever was tested with four times. The mean value was taken as the actual operating force, with the least significant difference being less than 0.05. The operating forces of operating levers were shown in Figure17. In order to facilitate comparison and analysis with theoretical values, the test values of various power capabilities of each operating lever are taken as the average value of the actual operating force of the operating lever as a whole. The theoretical values was compared with experimental results, and the results were shown in Figure 17.Figure 17
Comparison between theoretical operating force and actual operating force.According to Figure17, in addition to the forward and backward operating lever and the harvesting device joystick, the average operating force of the various types of levers designed in this paper is between 30.36 N and 42.71 N. Based on the 95th percentile of Chinese adult male hand, the best operating force is between 30 N and 40 N, so the actual lever operating force is in line with the ergonomics check. Since the forward and backward operating lever slot is stepped, the action is divided into two steps. The operating force should be appropriately reduced. Therefore, the actual average operating force is 13.19 N, which is in line with actual needs. The harvesting device joystick controls the operation and stop of the whole machine. In order to improve the fault tolerance of the machine and prevent the rice combine harvester from being stopped due to improper operation, the operating force should be appropriately designed to be larger. So, the actual operating force of 72.36 N is also in line with the actual demand.In addition to the cutting table integrated joystick and the harvesting device joystick, the operating force error of the remaining joystick members is 0.69% of the unloading grain and the reel lever. The maximum operating force is the forward and backward operating lever of 12.23%. It can be seen that the actual value of the lever is more in line with the theoretical design value. According to Table1, the utilization rate of the harvesting device is low. The design priority is only in the fifth, so the design error of the member is affordable. The design results of the joystick in this paper are reliable and achieve the expected results. The operating force of the joystick is suitable for the best operating force of the 95th percentile adult male in China.


#### 3.3.2. Bearing Stability of Crawler Chassis

The caterpillar chassis frame of the combine harvester is equipped with model combine harvester, which was developed and manufactured in Dongfeng agricultural machine Co., Ltd. The weight of the crawler chassis is 1500 kg. The test site was located in Changzhou town (119.93 N, 31.72 W), which is located in China’s southeast. The mean annual temperature and precipitation were 15.5°C and 1226 mm, respectively. The test pavement for the crawler chassis is a cement pavement. The test speed is three grades, which are 1 m/s, 1.5 m/s, and 2 m/s. In order to verify the stability of the processed crawler chassis under high load, it is necessary to test the straight speed of the harvester on the cement road surface. In addition, in order to simulate the actual movement of the harvester after bearing load, we adopt the method of gradually adding counterweights to the chassis frame of the harvester to make the chassis frame bear 4 t. The combine harvester performs the straight line driving ability test on the cement road surface, as shown in Figure18.Figure 18
Bearing stability test of the crawler chassis of the combine harvester.Three grades’ test speed was carried out for each gear position and the driving time was recorded. The test data of each gear are shown in Table6.Table 6
Rice combine harvester straight travel time (s).
No.
1
2
3
4
5
Mean value/s
Variance
Standard deviation
First gear (1 m/s)
55.65
55.72
55.34
55.60
55.43
55.53
0.1015
0.3186
Second gear (1.5 m/s)
35.78
35.55
35.71
35.30
35.65
35.60
0.1395
0.3735
Third gear (2 m/s)
27.12
26.86
27.15
26.81
26.95
27.03
0.1062
0.3259The travel time is converted to the travel speed at high load, as shown in Table7. According to the experimental data in Tables 6 and 7, the bearing stability of the crawler chassis designed in this paper is analyzed. The rice combine harvester equipped with the crawler self-propelled chassis designed in this paper was obtained.Table 7
High-load linear speed of the combine harvester.
No.
1
2
3
4
5
Mean value (m/s)
Variance
Standard deviation
First gear (1 m/s)
0.898
0.897
0.904
0.899
0.902
0.900
2.668
×
10
−
5
0.0052
Second gear (1.5 m/s)
1.397
1.406
1.400
1.416
1.403
1.404
2.189
×
10
−
4
0.0148
Third gear (2 m/s)
1.844
1.862
1.841
1.865
1.855
1.850
5.022
×
10
−
4
0.0224According to Tables6 and 7, the average running speed of the harvester on the cement pavement is 0.9 m/s, 1.4 m/s, and 1.85 m/s, respectively. The test data show that the gearbox is in actual operation. The transmission efficiency is about 90% to 93% of the design calculation. The load capacity of the crawler chassis can meet the expected requirements. The whole machine can be stably operated with the condition of load 4 t. The speed variance is close to 0, which is generally satisfied with test requirements.


## 3.1. Cab Variable Design of Crawler Chassis

### 3.1.1. Results of Operating Levers Variable Design

The connecting rod variable of unloading clutch operating lever and the reel operating lever arel2 = 75 mm and l3 = 400 mm, c = 10 mm is brought into equation (9), the rotation angle θ1 = 7.66° can be obtained, and the displacement of the rod is 55 mm. The connecting rod variable of the forward and backward operating lever are l2 = 45 mm and l3 = 270 mm, c = 20 mm with the input equation (9), the rotation angle θ2 = 26.44° can be obtained, and the displacement of the rod is 182 mm; shift lever’s variable l2 = 180 mm and l3 = 680 mm, c = 70 mm is brought in equation (9), the rotation angle θ3 = 22.94° can be obtained, and the rod displacement is 155 mm. The connecting rod variables of the cutting table integrated joystick l2 = 65 mm and l3 = 410 mm, c = 20 mm is brought in equation (9), the rotation angle θ4 = 17.9° can be obtained, and the displacement of the rod is 148 mm. The connecting rod variables of the harvesting device joystick l2 = 95 mm and l3 = 480 mm, c = 40 mm is brought in equation (9), the rotation angle θ5 = 24.95° can be obtained, and the displacement of the rod is 78 mm; the connecting rod variable of the brake joystick is l2 = 50 mm and l3 = 400 mm, c = 10 mm is brought in equation (9), the rotation angle θ6 = 11.53° can be obtained, and the displacement of the rod is 55 mm.The BC rod lengthl2, the CD rod length l3, the switch stroke c, the rotation angle θ, and the theoretical operating force F are substituted into equation (13) to obtain the length l1 of each rod handle, and the working variable of each rod are shown in – 4.Table 4
Design variable and theoretical operating force of the joystick.
No.
The evaluation object
Length of AB 11/mm
Length of BC l2/mm
Length of CD l3/mm
Switch strokec (mm)
Rotation angleθ/°
Displacement of the rod /mm
Theoretical operating forceF/N 1Unloading clutch operating lever reel operating lever28075400107.665532.02Forward and backward operating lever450452702026.4218211.553Shift lever4201806807020.0015443.934Cutting table integrated joystick350654102023.2114821.915Harvesting device joystick280954804018.247839.346Brake lever220504001011.545527.8


### 3.1.2. Chinese Adult Male Upper Limb Level Work Area Design

According to the data and analysis in Tables2 and 3, the 95th percentile upper limb horizontal operation area in China is obtained, as shown in Figure 12.Figure 12
Schematic diagram of horizontal working area of man’s upper limbs.As shown in Figure12, area I is a comfortable manipulation area, the range of which is the envelope area with the shoulder joint as the center and R400 as the radius. Area III is the effective operation area, which is equivalent to the range of upper limb function. Area IV is an expandable operation area, which is defined as the area that can be properly changed (inclined and bent) and the hand can be reached in the correct sitting position. Joystick location layout should meet within the scope of regional III. Surface height should be able to make the person’s upper arms naturally prolapse, which is in a state of relaxed and comfortable. Arm should be as far as possible under level or slightly oblique. This will reduce arm soreness. Based on the abovementioned analysis, an ideal relative position of the bars can be obtained, so as to design the overall space layout of the cab.


### 3.1.3. Design of Cab Maneuvering Space Layout

Combining the data in Tables2 and 3 with the corrections, the sum of the elbow height and the calf plus foot height of the lower man in the 50th percentile sitting position is 676 mm. Taking into account the amount of shoe and dressing correction (40 mm), the vertical distance between the elbow and foot of the 50th percentile man is 716 mm, and the height of the working surface is 500 mm, which is the height of the console. The best height is 178–203 mm above the H point (H point is the span point), and the vertical height of the lever handle position should be designed to be 100–250 mm higher than the console. Therefore, the designed reel operating lever is 160 mm higher than the console. The forward and backward operating lever is 250 mm higher than the console. The shift lever is 200 mm above the console. The brake lever is 100 mm higher than the console.According to the calculated steering angle of each lever and the specified height of levers higher than the console, the length of the lever stroke groove of the console can be determined. Through calculation, the slot length of the reel operating lever on the console is 40 mm (the data are rounded and the functional stroke is 33 mm). The upper end of the reel operating lever groove makes the reel lower, and the lower end raises the reel. The groove of cutting table integrated joystick is Mi-shaped. In order to simplify the processing, we design the groove to be a circle with a diameter of 85 mm. The left end of the groove turns the harvester left and the right end turns the harvester right, and the upper end makes the header and the lower end raises the header. The length of the forward and backward operating lever groove is 120 mm (bidirectional, stepped, and the functional stroke is 92 mm), the front section of the groove advances the harvester, the middle of the groove stops the harvester, and the rear end of the groove moves the harvester backward. The length of the shift lever groove on the console is 180 mm (the function stroke is 150 mm); the front section of the groove represents the standard speed, and the rear end of the groove represents low speed. The length of the brake lever groove is 145 mm, and the front section of the groove represents the state of small throttle; the rear end of the groove represents the state of large throttle.The control console in the cab is mainly composed of a side control panel, which is located on the left-hand side of the driver. The central bedplate is located directly in front of the driver. Therefore, the length, width, and thickness of the instrument panel of the central control console are 1100 mm, 180 mm, and 2 mm, respectively. The length, width, and thickness of the instrument panel of the measurement and control console are 1200 mm, 310 mm, and 2 mm, respectively. After manufacturing the grooves required for the instrument panel and levers, distribute the levers in the normal working area of the driver’s left and right hands. Taking the left and right shoulders of the driver as the center of the circle, the radius of 400 mm is the most suitable area for the distribution of the rods. The rods should not exceed the radius of a circle with the shoulder as the center and a radius of 550 mm. The overall space layout of the designed cab and the internal structure of the bar are shown in Figures13 and 14 below.Figure 13
Overall layout model of cab maneuvering space.Figure 14
Internal structure of the operating lever.


### 3.1.4. Stress and Strain Analysis of the Chassis Frame

The static analysis is mainly used to analyze the deformation and equivalent stress of the chassis after being loaded. According to the value of the total variables and the equivalent stress on the cloud map, the bearing capacity of each part of the chassis is analyzed [32]. Based on the previous meshing, loading and restraining of the chassis frame, the stress-strain cloud map is obtained as Figure 5.According to Figure5(a), it can be seen that the distribution of large stress is concentrated at the connection between the upper frame and the middle frame, the horizontal resistance of the crawler to the frame and the compression part of the grain box. So, the maximum stress is less than 173.25 Mpa. There is no stress concentration. The yield strength of Q235 material is 235 Mpa, which is meeting the requirements of Q235. According to Figure 5(b), the most serious deformation of the chassis frame is the red part, which is about 9.2504 mm. Because of full load, the bearing part of the grain box is the largest pressure. The supporting beam of the load-bearing part is a cantilever beam structure, where the bending moment is large and the deformation is the most obvious. The second largest part of the deformation is the fuel tank, and the deformation is 1.0278 to 5.1391 mm. This is because the fuel tank is at the farthest edge of the frame, and there is not enough support beams in the longitudinal direction to share the load. The third largest part of the deformation is the cab, and the total deformation is 0 to 5.1391 mm. This is because the entire bridge support is also in a suspended state, with insufficient support, resulting in a relatively large deformation. So, when the total weight is about 4 t in full load, the maximum shape variable is 9.2504 mm. The strength and stiffness of the chassis frame meet the design requirements.


## 3.1.1. Results of Operating Levers Variable Design

The connecting rod variable of unloading clutch operating lever and the reel operating lever arel2 = 75 mm and l3 = 400 mm, c = 10 mm is brought into equation (9), the rotation angle θ1 = 7.66° can be obtained, and the displacement of the rod is 55 mm. The connecting rod variable of the forward and backward operating lever are l2 = 45 mm and l3 = 270 mm, c = 20 mm with the input equation (9), the rotation angle θ2 = 26.44° can be obtained, and the displacement of the rod is 182 mm; shift lever’s variable l2 = 180 mm and l3 = 680 mm, c = 70 mm is brought in equation (9), the rotation angle θ3 = 22.94° can be obtained, and the rod displacement is 155 mm. The connecting rod variables of the cutting table integrated joystick l2 = 65 mm and l3 = 410 mm, c = 20 mm is brought in equation (9), the rotation angle θ4 = 17.9° can be obtained, and the displacement of the rod is 148 mm. The connecting rod variables of the harvesting device joystick l2 = 95 mm and l3 = 480 mm, c = 40 mm is brought in equation (9), the rotation angle θ5 = 24.95° can be obtained, and the displacement of the rod is 78 mm; the connecting rod variable of the brake joystick is l2 = 50 mm and l3 = 400 mm, c = 10 mm is brought in equation (9), the rotation angle θ6 = 11.53° can be obtained, and the displacement of the rod is 55 mm.The BC rod lengthl2, the CD rod length l3, the switch stroke c, the rotation angle θ, and the theoretical operating force F are substituted into equation (13) to obtain the length l1 of each rod handle, and the working variable of each rod are shown in – 4.Table 4
Design variable and theoretical operating force of the joystick.
No.
The evaluation object
Length of AB 11/mm
Length of BC l2/mm
Length of CD l3/mm
Switch strokec (mm)
Rotation angleθ/°
Displacement of the rod /mm
Theoretical operating forceF/N 1Unloading clutch operating lever reel operating lever28075400107.665532.02Forward and backward operating lever450452702026.4218211.553Shift lever4201806807020.0015443.934Cutting table integrated joystick350654102023.2114821.915Harvesting device joystick280954804018.247839.346Brake lever220504001011.545527.8


## 3.1.2. Chinese Adult Male Upper Limb Level Work Area Design

According to the data and analysis in Tables2 and 3, the 95th percentile upper limb horizontal operation area in China is obtained, as shown in Figure 12.Figure 12
Schematic diagram of horizontal working area of man’s upper limbs.As shown in Figure12, area I is a comfortable manipulation area, the range of which is the envelope area with the shoulder joint as the center and R400 as the radius. Area III is the effective operation area, which is equivalent to the range of upper limb function. Area IV is an expandable operation area, which is defined as the area that can be properly changed (inclined and bent) and the hand can be reached in the correct sitting position. Joystick location layout should meet within the scope of regional III. Surface height should be able to make the person’s upper arms naturally prolapse, which is in a state of relaxed and comfortable. Arm should be as far as possible under level or slightly oblique. This will reduce arm soreness. Based on the abovementioned analysis, an ideal relative position of the bars can be obtained, so as to design the overall space layout of the cab.


## 3.1.3. Design of Cab Maneuvering Space Layout

Combining the data in Tables2 and 3 with the corrections, the sum of the elbow height and the calf plus foot height of the lower man in the 50th percentile sitting position is 676 mm. Taking into account the amount of shoe and dressing correction (40 mm), the vertical distance between the elbow and foot of the 50th percentile man is 716 mm, and the height of the working surface is 500 mm, which is the height of the console. The best height is 178–203 mm above the H point (H point is the span point), and the vertical height of the lever handle position should be designed to be 100–250 mm higher than the console. Therefore, the designed reel operating lever is 160 mm higher than the console. The forward and backward operating lever is 250 mm higher than the console. The shift lever is 200 mm above the console. The brake lever is 100 mm higher than the console.According to the calculated steering angle of each lever and the specified height of levers higher than the console, the length of the lever stroke groove of the console can be determined. Through calculation, the slot length of the reel operating lever on the console is 40 mm (the data are rounded and the functional stroke is 33 mm). The upper end of the reel operating lever groove makes the reel lower, and the lower end raises the reel. The groove of cutting table integrated joystick is Mi-shaped. In order to simplify the processing, we design the groove to be a circle with a diameter of 85 mm. The left end of the groove turns the harvester left and the right end turns the harvester right, and the upper end makes the header and the lower end raises the header. The length of the forward and backward operating lever groove is 120 mm (bidirectional, stepped, and the functional stroke is 92 mm), the front section of the groove advances the harvester, the middle of the groove stops the harvester, and the rear end of the groove moves the harvester backward. The length of the shift lever groove on the console is 180 mm (the function stroke is 150 mm); the front section of the groove represents the standard speed, and the rear end of the groove represents low speed. The length of the brake lever groove is 145 mm, and the front section of the groove represents the state of small throttle; the rear end of the groove represents the state of large throttle.The control console in the cab is mainly composed of a side control panel, which is located on the left-hand side of the driver. The central bedplate is located directly in front of the driver. Therefore, the length, width, and thickness of the instrument panel of the central control console are 1100 mm, 180 mm, and 2 mm, respectively. The length, width, and thickness of the instrument panel of the measurement and control console are 1200 mm, 310 mm, and 2 mm, respectively. After manufacturing the grooves required for the instrument panel and levers, distribute the levers in the normal working area of the driver’s left and right hands. Taking the left and right shoulders of the driver as the center of the circle, the radius of 400 mm is the most suitable area for the distribution of the rods. The rods should not exceed the radius of a circle with the shoulder as the center and a radius of 550 mm. The overall space layout of the designed cab and the internal structure of the bar are shown in Figures13 and 14 below.Figure 13
Overall layout model of cab maneuvering space.Figure 14
Internal structure of the operating lever.


## 3.1.4. Stress and Strain Analysis of the Chassis Frame

The static analysis is mainly used to analyze the deformation and equivalent stress of the chassis after being loaded. According to the value of the total variables and the equivalent stress on the cloud map, the bearing capacity of each part of the chassis is analyzed [32]. Based on the previous meshing, loading and restraining of the chassis frame, the stress-strain cloud map is obtained as Figure 5.According to Figure5(a), it can be seen that the distribution of large stress is concentrated at the connection between the upper frame and the middle frame, the horizontal resistance of the crawler to the frame and the compression part of the grain box. So, the maximum stress is less than 173.25 Mpa. There is no stress concentration. The yield strength of Q235 material is 235 Mpa, which is meeting the requirements of Q235. According to Figure 5(b), the most serious deformation of the chassis frame is the red part, which is about 9.2504 mm. Because of full load, the bearing part of the grain box is the largest pressure. The supporting beam of the load-bearing part is a cantilever beam structure, where the bending moment is large and the deformation is the most obvious. The second largest part of the deformation is the fuel tank, and the deformation is 1.0278 to 5.1391 mm. This is because the fuel tank is at the farthest edge of the frame, and there is not enough support beams in the longitudinal direction to share the load. The third largest part of the deformation is the cab, and the total deformation is 0 to 5.1391 mm. This is because the entire bridge support is also in a suspended state, with insufficient support, resulting in a relatively large deformation. So, when the total weight is about 4 t in full load, the maximum shape variable is 9.2504 mm. The strength and stiffness of the chassis frame meet the design requirements.


## 3.2. Physical Assembly and Production

### 3.2.1. Integral Assembly of Mechanical Model

From the perspective of the overall configuration of the whole machine, the cab is placed above the frame of crawler on the right side of the crawler chassis. The space adjustment of each solid module is carried out to ensure reasonable space configuration and balanced center of gravity configuration of the whole machine. The integral assembly of crawler chassis is shown in Figure15.Figure 15
Integral assembly of crawler chassis.


### 3.2.2. Production of Test Prototype

According to the variable shown in Tables2, 3, and 5, each device was developed and manufactured in Dongfeng agricultural machine Co., Ltd. The chassis frame is welded with square and rectangular pipes of different specifications such as 30 × 30 mm, 40 × 40 mm, and 40 × 60 mm. The chassis frame is 3.807 m long, 2.163 m wide, and 1.036 m high. The suspension plate width of the rubber track is 340 mm. The grounding length is 1700 mm. The total length is 3900 mm. The full-load average grounding pressure ratio is 33.9 kpa. The size of the cab is 1400 × 1100 × 1350 mm, which is placed above the track on the right side of the chassis frame to complete the overall assembly. The actual picture of crawler chassis of rice combine harvester is shown in Figure 16.Table 5
Main component variable of the combine harvester.
Main load
Grain box
Cab
Engine
Oil tank
Cylinder
Threshing drum
Battery
Working weight (kg)
1771
265
300
85
359.4
1260
50
Bearing area (m2)
0.0560
0.1760
0.0264
0.1350
0.0142
0.1585
0.0154
Intensity of full-load pressure (MPa)
0.3098
0.0150
0.1040
0.0617
0.2480
0.0779
0.0319
Allowable load (N)
20826.9 6
3116.4
3528
999.6
4226.88
14817.6
588Figure 16
Production of crawler chassis of the combine harvester.


## 3.2.1. Integral Assembly of Mechanical Model

From the perspective of the overall configuration of the whole machine, the cab is placed above the frame of crawler on the right side of the crawler chassis. The space adjustment of each solid module is carried out to ensure reasonable space configuration and balanced center of gravity configuration of the whole machine. The integral assembly of crawler chassis is shown in Figure15.Figure 15
Integral assembly of crawler chassis.


## 3.2.2. Production of Test Prototype

According to the variable shown in Tables2, 3, and 5, each device was developed and manufactured in Dongfeng agricultural machine Co., Ltd. The chassis frame is welded with square and rectangular pipes of different specifications such as 30 × 30 mm, 40 × 40 mm, and 40 × 60 mm. The chassis frame is 3.807 m long, 2.163 m wide, and 1.036 m high. The suspension plate width of the rubber track is 340 mm. The grounding length is 1700 mm. The total length is 3900 mm. The full-load average grounding pressure ratio is 33.9 kpa. The size of the cab is 1400 × 1100 × 1350 mm, which is placed above the track on the right side of the chassis frame to complete the overall assembly. The actual picture of crawler chassis of rice combine harvester is shown in Figure 16.Table 5
Main component variable of the combine harvester.
Main load
Grain box
Cab
Engine
Oil tank
Cylinder
Threshing drum
Battery
Working weight (kg)
1771
265
300
85
359.4
1260
50
Bearing area (m2)
0.0560
0.1760
0.0264
0.1350
0.0142
0.1585
0.0154
Intensity of full-load pressure (MPa)
0.3098
0.0150
0.1040
0.0617
0.2480
0.0779
0.0319
Allowable load (N)
20826.9 6
3116.4
3528
999.6
4226.88
14817.6
588Figure 16
Production of crawler chassis of the combine harvester.


## 3.3. Comparative Analysis of Theoretical Design and Experimental Results

### 3.3.1. Joystick Design and Control Force Test

The operating force of the operating lever was tested with four times. The mean value was taken as the actual operating force, with the least significant difference being less than 0.05. The operating forces of operating levers were shown in Figure17. In order to facilitate comparison and analysis with theoretical values, the test values of various power capabilities of each operating lever are taken as the average value of the actual operating force of the operating lever as a whole. The theoretical values was compared with experimental results, and the results were shown in Figure 17.Figure 17
Comparison between theoretical operating force and actual operating force.According to Figure17, in addition to the forward and backward operating lever and the harvesting device joystick, the average operating force of the various types of levers designed in this paper is between 30.36 N and 42.71 N. Based on the 95th percentile of Chinese adult male hand, the best operating force is between 30 N and 40 N, so the actual lever operating force is in line with the ergonomics check. Since the forward and backward operating lever slot is stepped, the action is divided into two steps. The operating force should be appropriately reduced. Therefore, the actual average operating force is 13.19 N, which is in line with actual needs. The harvesting device joystick controls the operation and stop of the whole machine. In order to improve the fault tolerance of the machine and prevent the rice combine harvester from being stopped due to improper operation, the operating force should be appropriately designed to be larger. So, the actual operating force of 72.36 N is also in line with the actual demand.In addition to the cutting table integrated joystick and the harvesting device joystick, the operating force error of the remaining joystick members is 0.69% of the unloading grain and the reel lever. The maximum operating force is the forward and backward operating lever of 12.23%. It can be seen that the actual value of the lever is more in line with the theoretical design value. According to Table1, the utilization rate of the harvesting device is low. The design priority is only in the fifth, so the design error of the member is affordable. The design results of the joystick in this paper are reliable and achieve the expected results. The operating force of the joystick is suitable for the best operating force of the 95th percentile adult male in China.


### 3.3.2. Bearing Stability of Crawler Chassis

The caterpillar chassis frame of the combine harvester is equipped with model combine harvester, which was developed and manufactured in Dongfeng agricultural machine Co., Ltd. The weight of the crawler chassis is 1500 kg. The test site was located in Changzhou town (119.93 N, 31.72 W), which is located in China’s southeast. The mean annual temperature and precipitation were 15.5°C and 1226 mm, respectively. The test pavement for the crawler chassis is a cement pavement. The test speed is three grades, which are 1 m/s, 1.5 m/s, and 2 m/s. In order to verify the stability of the processed crawler chassis under high load, it is necessary to test the straight speed of the harvester on the cement road surface. In addition, in order to simulate the actual movement of the harvester after bearing load, we adopt the method of gradually adding counterweights to the chassis frame of the harvester to make the chassis frame bear 4 t. The combine harvester performs the straight line driving ability test on the cement road surface, as shown in Figure18.Figure 18
Bearing stability test of the crawler chassis of the combine harvester.Three grades’ test speed was carried out for each gear position and the driving time was recorded. The test data of each gear are shown in Table6.Table 6
Rice combine harvester straight travel time (s).
No.
1
2
3
4
5
Mean value/s
Variance
Standard deviation
First gear (1 m/s)
55.65
55.72
55.34
55.60
55.43
55.53
0.1015
0.3186
Second gear (1.5 m/s)
35.78
35.55
35.71
35.30
35.65
35.60
0.1395
0.3735
Third gear (2 m/s)
27.12
26.86
27.15
26.81
26.95
27.03
0.1062
0.3259The travel time is converted to the travel speed at high load, as shown in Table7. According to the experimental data in Tables 6 and 7, the bearing stability of the crawler chassis designed in this paper is analyzed. The rice combine harvester equipped with the crawler self-propelled chassis designed in this paper was obtained.Table 7
High-load linear speed of the combine harvester.
No.
1
2
3
4
5
Mean value (m/s)
Variance
Standard deviation
First gear (1 m/s)
0.898
0.897
0.904
0.899
0.902
0.900
2.668
×
10
−
5
0.0052
Second gear (1.5 m/s)
1.397
1.406
1.400
1.416
1.403
1.404
2.189
×
10
−
4
0.0148
Third gear (2 m/s)
1.844
1.862
1.841
1.865
1.855
1.850
5.022
×
10
−
4
0.0224According to Tables6 and 7, the average running speed of the harvester on the cement pavement is 0.9 m/s, 1.4 m/s, and 1.85 m/s, respectively. The test data show that the gearbox is in actual operation. The transmission efficiency is about 90% to 93% of the design calculation. The load capacity of the crawler chassis can meet the expected requirements. The whole machine can be stably operated with the condition of load 4 t. The speed variance is close to 0, which is generally satisfied with test requirements.


## 3.3.1. Joystick Design and Control Force Test

The operating force of the operating lever was tested with four times. The mean value was taken as the actual operating force, with the least significant difference being less than 0.05. The operating forces of operating levers were shown in Figure17. In order to facilitate comparison and analysis with theoretical values, the test values of various power capabilities of each operating lever are taken as the average value of the actual operating force of the operating lever as a whole. The theoretical values was compared with experimental results, and the results were shown in Figure 17.Figure 17
Comparison between theoretical operating force and actual operating force.According to Figure17, in addition to the forward and backward operating lever and the harvesting device joystick, the average operating force of the various types of levers designed in this paper is between 30.36 N and 42.71 N. Based on the 95th percentile of Chinese adult male hand, the best operating force is between 30 N and 40 N, so the actual lever operating force is in line with the ergonomics check. Since the forward and backward operating lever slot is stepped, the action is divided into two steps. The operating force should be appropriately reduced. Therefore, the actual average operating force is 13.19 N, which is in line with actual needs. The harvesting device joystick controls the operation and stop of the whole machine. In order to improve the fault tolerance of the machine and prevent the rice combine harvester from being stopped due to improper operation, the operating force should be appropriately designed to be larger. So, the actual operating force of 72.36 N is also in line with the actual demand.In addition to the cutting table integrated joystick and the harvesting device joystick, the operating force error of the remaining joystick members is 0.69% of the unloading grain and the reel lever. The maximum operating force is the forward and backward operating lever of 12.23%. It can be seen that the actual value of the lever is more in line with the theoretical design value. According to Table1, the utilization rate of the harvesting device is low. The design priority is only in the fifth, so the design error of the member is affordable. The design results of the joystick in this paper are reliable and achieve the expected results. The operating force of the joystick is suitable for the best operating force of the 95th percentile adult male in China.


## 3.3.2. Bearing Stability of Crawler Chassis

The caterpillar chassis frame of the combine harvester is equipped with model combine harvester, which was developed and manufactured in Dongfeng agricultural machine Co., Ltd. The weight of the crawler chassis is 1500 kg. The test site was located in Changzhou town (119.93 N, 31.72 W), which is located in China’s southeast. The mean annual temperature and precipitation were 15.5°C and 1226 mm, respectively. The test pavement for the crawler chassis is a cement pavement. The test speed is three grades, which are 1 m/s, 1.5 m/s, and 2 m/s. In order to verify the stability of the processed crawler chassis under high load, it is necessary to test the straight speed of the harvester on the cement road surface. In addition, in order to simulate the actual movement of the harvester after bearing load, we adopt the method of gradually adding counterweights to the chassis frame of the harvester to make the chassis frame bear 4 t. The combine harvester performs the straight line driving ability test on the cement road surface, as shown in Figure18.Figure 18
Bearing stability test of the crawler chassis of the combine harvester.Three grades’ test speed was carried out for each gear position and the driving time was recorded. The test data of each gear are shown in Table6.Table 6
Rice combine harvester straight travel time (s).
No.
1
2
3
4
5
Mean value/s
Variance
Standard deviation
First gear (1 m/s)
55.65
55.72
55.34
55.60
55.43
55.53
0.1015
0.3186
Second gear (1.5 m/s)
35.78
35.55
35.71
35.30
35.65
35.60
0.1395
0.3735
Third gear (2 m/s)
27.12
26.86
27.15
26.81
26.95
27.03
0.1062
0.3259The travel time is converted to the travel speed at high load, as shown in Table7. According to the experimental data in Tables 6 and 7, the bearing stability of the crawler chassis designed in this paper is analyzed. The rice combine harvester equipped with the crawler self-propelled chassis designed in this paper was obtained.Table 7
High-load linear speed of the combine harvester.
No.
1
2
3
4
5
Mean value (m/s)
Variance
Standard deviation
First gear (1 m/s)
0.898
0.897
0.904
0.899
0.902
0.900
2.668
×
10
−
5
0.0052
Second gear (1.5 m/s)
1.397
1.406
1.400
1.416
1.403
1.404
2.189
×
10
−
4
0.0148
Third gear (2 m/s)
1.844
1.862
1.841
1.865
1.855
1.850
5.022
×
10
−
4
0.0224According to Tables6 and 7, the average running speed of the harvester on the cement pavement is 0.9 m/s, 1.4 m/s, and 1.85 m/s, respectively. The test data show that the gearbox is in actual operation. The transmission efficiency is about 90% to 93% of the design calculation. The load capacity of the crawler chassis can meet the expected requirements. The whole machine can be stably operated with the condition of load 4 t. The speed variance is close to 0, which is generally satisfied with test requirements.


## 4. Conclusions

(1)
The results of stress-strain cloud diagram obtained by Finite Element Analysis show that under the low-speed full-load condition, the maximum strain of the chassis frame is the load-bearing part of the grain box. The load-bearing part of the oil tank has a shape variable of 1.0278∼5.1391 mm, which are all within a reasonable controllable range. The stress distribution is concentrated at the joint between the upper frame and the middle frame, the horizontal resistance of the track to the frame, and the pressure of the grain box. The maximum stress is less than 173.25 MPa. The strength is checked and meets the design requirements.
(2)
When the designed track grounding length is 1.7 m, the steering ratio is 1.185 and the crawler chassis is 4 t; it is applied to the rice combine harvester at the first speed of 1 m/s, 1.5 m/s, and 2 m/s. The driving test results show that the maximum variance of the combine harvester speed is 5.022 × 10–4. The maximum standard deviation is 0.0224, which indicates that the crawler chassis still has good driving stability and good carrying performance at high load.
(3)
The test results of man-machine test show that the average operating force of all kinds of operating levers designed in this paper is between 30.36 N and 42.71 N, which meets the best operating force of the hands of adult males in the 95th percent in China. The operating force test value of the forward and backward lever is 13.19 N, which is designed to match its stepped groove. The experimental value of joystick is to improve the fault tolerance rate of the rice combine harvester operated by the hand, so the operating force is in line with the ergonomic design. The operation force error is small, which is reasonable and reliable.



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*Source: 7610767-2020-05-04.xml*