Design and realisation of a motorized beans shelling machine

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Recognizing the significant value and potential of this crop has led to the push for creating a mechanized bean shelling system as part of modern agricultural planning. This study focused on design and realisation of beans shelling machine. The machine was designed and realisation was achieved using appropriate engineering materials selected for various parts of the machine. This machine incorporated an air chamber system which was used in air production for waste disposal. Peeled beans was collected via a collecting vessel. Pulleys were used as speed reducers to transmit power and movement in order to enhance efficiency of the machine and the preservation of the good quality product. The machine performed well when it is motorised with a 2HP motor 1400rpm and a turning speed of 950rpm and average torque of 4.944Nm. Pulley groove selected at 206mm. we obtained for 92.7% beans peeling efficiency with a 630.32 kg/h of beans shelled. design realisation beans shelling machine Figures Figure 1 Figure 2 Figure 3 Figure 4 Figure 5 Figure 6 Figure 7 Figure 8 Figure 9 Figure 10 Figure 11 Figure 12 1. Introduction Common beans ( Phaseolus vulgaris L.) are a major food and income source in many developing regions. Their high nutritional value—consisting of proteins, minerals, vitamins, and dietary fibre—makes them a key component of diets in sub-Saharan Africa. In Cameroon, bean cultivation has expanded considerably, positioning the country as the seventh-largest producer in the region. National production rose from approximately 365,295 metric tons in 2017 to 373,624 metric tons in 2021, driven largely by population growth and increasing urban demand. However, this rise in production has not translated into lower market prices, largely due to persistent constraints in the production and post-harvest chain. These challenges include limited access to improved seed varieties, outdated farming tools, declining soil fertility, inadequate pest control, and substantial post-harvest losses. Manual shelling remains one of the most labor-intensive bottlenecks, contributing significantly to inefficiencies in the value chain. The introduction of agricultural machinery has been widely recognized as a means to improve efficiency and product quality. Olaoye [ 8 ] highlighted that although mechanical shelling technologies may involve high initial investment, they reduce labor intensity, maintain kernel quality, and minimize losses compared with traditional methods. This has encouraged several research efforts aimed at developing cost-effective shelling machines, particularly using locally available materials. Unuigbe et al. [ 9 ] designed and constructed a bean sheller using local materials, supported by detailed component design and fabrication drawings. Their machine achieved a shelling efficiency of 81.3% with a processing capacity of 100 kg/h, demonstrating the feasibility of low-cost mechanical solutions. Ilori et al. [ 10 ] investigated ergonomic factors in hand-operated shellers, identifying that operator characteristics such as age, weight, and arm length significantly influence shelling efficiency, an important consideration for manually powered devices. Other studies have focused on optimizing machine design for higher performance. Ashwin and Shaik [ 11 ] developed a hand-operated cylinder–concave sheller that reached a shelling efficiency of 99.56% at 12% moisture content and 130 kg/h feed rate, with minimal unshelled grains and acceptable grain damage. Engineers at the USDA [ 12 ] designed an experimental gentle-handling sheller, which performed well at 15% moisture content but suffered from issues related to belt durability, low throughput, and reduced efficiency at higher moisture levels. Fox [ 13 ] proposed a rubber-roller sheller based on rolling and squeezing principles; however, it faced feeding limitations and did not perform satisfactorily on unhusked pods. Research on similar post-harvest processes provides useful insight into efficiency gains from mechanization. Karthickumar et al. [ 14 ] developed a continuous tamarind deseeding machine with a throughput of 75 kg/h and a maximum efficiency of 89.15%, reducing both cost and processing time relative to manual methods. Similarly, Hiregoudar and Udhayakumar [ 15 ] found that mechanical deseeding significantly increases output compared with traditional techniques, although at the cost of higher mechanical damage. Additional studies by Aluko [ 16 ], Babatunde et al. [ 17 ], and Uadia and Ogbu [ 18 ] focused on the design, fabrication, and evaluation of bean shelling machines with the aim of improving shelling efficiency, reducing processing time, and minimizing losses. These works collectively emphasize methodologies for machine design and the potential benefits of mechanization in bean processing. A review of the literature shows that while many prototypes have been developed, several challenges persist: Low shelling efficiency in early designs, Limited processing capacity, restricting commercial use, High levels of grain damage, often linked to bean size variability, Mechanical limitations, such as poor feeding systems or fragile components, Lack of standardization, with many machines remaining at prototype stage. Given these limitations, there is a clear need for a more efficient, robust, and commercially viable bean shelling machine adapted to local conditions. The current study responds to this need by designing and developing a locally fabricated sheller capable of improving throughput, reducing mechanical damage, and supporting wider adoption of mechanized post-harvest technologies. 2. Materials and method. 2.1 Design Consideration The design and development of a bean shelling machine must consider several important factors, including product quality, material selection, and process efficiency. Product quality is evaluated based on the preservation of the beans’ physical and chemical properties. The construction materials should be resistant to corrosion, wear, and tear, while also being strong, readily available, and affordable. Other key considerations include the machine’s structural stability, ensuring it remains rigid during operation, and its ability to sort, meaning the separation of shelled beans into uniform aggregates within the shelling chamber. Affordability is also crucial, enabling farmers to compare the machine’s investment and maintenance costs with those of imported alternatives. 2.2. Conceptual design AutoCAD software was used to design components and to assembly them for the geometrical model of the machine. It was also used to simulate the rigidity of the frame in other to choose the suitable materials that could withstand the loads and preserve the stability. Figures 1and 2 show respectively the exploded and isomeric views of the machine designed. 2.3. Design analysis and calculations The design of various component parts of shelling machine is governed by physical, mechanical and engineering properties of beans. Others are the mechanism of rotating shaft over the concave at a specific clearance for the downward movement of the shelled grains. We are going to present the design analysis and calculations for major component parts. 2.3.1. Frame The two primary factors considered in selecting the frame material were weight and strength, as the frame would be subjected to compressive forces and torque. In this study, a hollow square steel tube (S235JR, 16 mm × 5 mm) was used to provide the necessary rigidity. The frame components were fabricated through cutting with an angle grinder, and the assembly was completed using the MIG/MAG welding process. 2.3.2. Hopper The hopper is designed to be fed in a horizontal position only. The material used for the construction is carbon steel S235 JR 2000x 1000 sheet metal, which is readily available in the market and relatively affordable. 2.3.3. Beans inlet vessel It was done by carbon steel S235 JR 2000x 1000 Cutting via a shearing machine and Bending via an angle bending machine with the dimensions of 470mm x 285.69mm. 2.3.4.. Sieve chamber connected to mechanism It has the dimensions of 850mm x 360mm realized with carbon steel by cutting using the shearing machine. 2.3.5. Blower It is the composition of the fan system with fan blades of 500mm x100mm enclosed in the shaft realized by Cutting/Cleaning and the Air chamber of 767mm x 200mm, Radius 80mm realized with cutting, Rolling and Welding process. 2.3.6. Design of shaft It is a cylindrical solid rod for transmitting motion through a set of load carried on it. The design is based on fluctuating torque, bending moment and shearing force. Determination of Maximum Bending Moment 𝑀𝑏 The maximum bending moment is given by Eq. ( 1 ) $$\:Mb=\sqrt{{\left(\text{M}\text{B}\text{V}\right)}^{2}-{\left(\text{M}\text{B}\text{H}\right)}^{2}}$$ 1 Where 𝑀𝐵𝑉 is the vertical bending moment (Nm).and 𝑀𝐵𝐻 the horizontal bending moment (Nm). Figure 3 bellow presents the different loads acting on the shaft. W represents the centrifugal force of the pulley, q is the uniformly distributed loads in housing chamber due to weight of beans and R A , R B are reactions of the bearings. Figure 4 presents forces acting on the shaft to be calculated. Calculations: Weight of pulley W= 1kg 𝐹 𝐶 = 1kg x 10 = 10N Weight of beans M= 𝜌𝑉 = 𝜋𝐷 2 𝐿𝜌 =3.14 x 0.32 𝑥 1 𝑥 24 = 6.7kg 𝐹 𝐷 = 6.7kg x 10 = 67N Taking moment about R A : -10N x 0.25m -R B x 1m + 67N x 0.5m = 0 -2.5- RB + 33.5 = 0 R B = 31N R A =46N Figure 5 presents the vertical loading diagram At C, MBV = 0 At A, when x = 0.25 m MBV = 10 x 0.25 = 2.5Nm At D, when x = 0.75 m MBV = (10 x 0.75) – (46 x 0.5) MBV = − 15.5Nm Figure 6 presents vertical bending moment diagram. Calculations of horizontal bending moment Figure 7 presents the Horizontal loading. From Fig. 7 , taking moment about R B : 0 = 10N x 0.25m + R C x 1m; 0 = 2.5 + R C R C = − 2.5N R B + R C = 10N, R B = 12.5 N Figures 8 and 9 present horizontal loading force diagram and horizontal bending moment diagram respectively. At A, MBH = 0 At B, when x = 0.23 m MBH = 10 x 0.25 = 2.5Nm At C, when x = 1.25 m MBH = (10 x 1.25) – (12.5 x 1) MBH = 0 Nm Therefore the maximum bending moment is: M𝑏 = \(\:\sqrt{{\left(15.5\right)}^{2}-{\left(2.5\right)}^{2}}\) =15.70 Nm Determination of Torsional Moment, Mt The torsional moment, Mt is given by Mt = F D x r where r is the length of the sprike tooth linked on the shaft by welding process and constitute shelling mechanism. The diagram is presented on Fig. 10 bellow. Mt = 6.7 x 0.2 = 1,34N.m • Determination of shaft diameter For proper designing there is need to determine the shaft diameter, Eq. ( 2 ) was adopted: $$\:{d}^{3}=\frac{16}{\pi\:\delta\:s}{\left[{\left({K}_{b}{M}_{b}\right)}^{2}+{\left({K}_{t}{M}_{t}\right)}^{2}\right]}^{\frac{1}{2}}$$ 2 where d is diameter of shaft (mm), K b are bending moment fatigue and shock, K t are fatigue and combined factor for torsional moment, M b are resultant bending moment (Nm), Mt are resultant torsional moment (Nm), δsy are allowable bending stress (MN m − 2 ). Assumptions δs = 47 x 10 6 N/m K t =K b =1.5 $$\:{d}^{3}=\frac{16}{47\:\text{x}\:106\:\pi\:}{\left[{\left(1.5\text{x}15.7\:\right)}^{2}+{\left(\:1.5\text{x}1.34\right)}^{2}\right]}^{\frac{1}{2}}$$ d = 0.01644m We should choice a diameter of 20mm 2.3.7. Materials selection • Power requirement of motorized beans Shelling. The Power P (W) requirement was calculated based on the motor and belt efficiency of 70% and 75% respectively using Eq. (3). P= \(\:\frac{\text{P}{\prime\:}}{\text{m}\text{o}\text{t}\text{o}\text{r}\:\text{e}\text{f}\text{f}\text{i}\text{c}\text{i}\text{e}\text{n}\text{c}\text{y}\:\text{x}\:\text{b}\text{e}\text{l}\text{t}\:\text{e}\text{f}\text{f}\text{i}\text{c}\text{i}\text{e}\text{n}\text{c}\text{y}\:}\text{x}\:\text{s}\text{a}\text{f}\text{e}\text{t}\text{y}\:\text{f}\text{a}\text{c}\text{t}\text{o}\text{r}\:\) (3) Where P’ is the theorical power (W) P’= F × V Where F is force of shelling (N), V are velocity (m/s). V = 𝜋DN According to [ 17 ], the shelling speed that will give very low mechanical damage, but high threshing output is within the range of 950 revolutions per minute. Let’s us take N = 950 rpm and safety factor equal to 2 P’= 15.5 × 3.14 x 0.4 x 950/60 = 368W P= \(\:\frac{368}{70\text{%}\:\text{x}\:75\text{%}}\:\:\times\:2\) P= 1400W Then the motor power should be around 2HP since 1HP=737W • Determination of the diameter of the driven pulley To calculate the diameter D of the driven pulley we use the Fig. 11 representing the pulleys-belt system. The Eq. (5) presents the relationship between the diameters and rpm of the two pulleys. N 1 d = N 2 D (5) N 1 speed of driver=1400rpm and N 2 speed of driven D diameter of \(\:d\) riven and d diameter of driver=140mm \(\:D=\frac{{N}_{1}d}{{N}_{2}}\:=\:\frac{1400\text{X}140}{850}\:=\:\) 206 D = 206 mm 2.4.1. V-belt selection Length of belt For a motor rating of 0.7W, the suitable choice is class A with a pitch length of 1.06mm according to IS: 2494–1974 standard. Top width of 13mm. we choice a standard length of 925 mm. Centre Distance of Belt The length of the belt is given by the Eq. (6); L = 2x + (π/2)(D + d) + (D – d) 2/ (4x) (6) Where; L = length of belt, D and d are the diameter of the driven and driving pulleys respectively, x = centre-to-centre distance between the driving and driven pulleys. 925 = 2x + (π/2)(206 + 130) + (206–130)2/(4x) x = 200mm The power transmitted by belt is given by Eq. (7) P = (T1 – T2)V (7) V = (πDN)/60. Also, T 1 /T 2 = exp(µθ cosec β), where: β = groove semi-angle 2β = 34; θ = angle of lap; α = angle of contact at the smaller pulley; µ = coefficient of friction. The coefficient of friction for rubber belt on cast iron or steel operating on dry surface is µ = 0.3. The angle of lap for open V-belt drive is given as: x = distance between pulleys; d = diameter of smaller pulley; D = diameter of bigger pulley. θ = (180–18.4) x π/180 = 2.81rad P = πDN (T 1 – T 2 )/60 T 1 – T 2 = \(\:\frac{60\text{X}1400}{3.14\text{X}0.130\text{x}1500}=137\) T 1 /T 2 = \(\:\:\) exp(0.3x2.81x cosec17) = 2.2 \(\:\frac{\:{T}_{2+137}\:}{{T}_{2}}\) =2.2 T 2 =114N T 1 =250N 3. Results and Discussions Figure 12 is the beans shelling machine realised. 3.1. Working principle of the beans shelling machine Untreated beans is fed into the hopper then channels the beans to the hopper top cover through the shield box. The shield box prevents beans from pouring and therefore channels the beans to the rotor mechanism. The mechanism is made up of a shaft with square tubes welded on the surface of the shaft. This is the main part of the machine because this causes the force used in beating the beans. It is enclosed to the bottom hopper and a sieve vessel. The sieve vessel contains holes drilled at 10mm which serves as channel for the peeled beans to pass through. The bottom hopper contains an outlet where the peeled beans pass through. The peeled beans then fall on the sieve plate. The sieve plate is connected to the hopper bottom cover via connecting rod. The connecting rod is linked to the hopper bottom cover and the sieve plate via drilled holes of 10mm screwed properly to ensure stability. The stability of the plate is reinforced by sieve carrier below the sieve plate. As the peeled beans falls on the sieve plate, air issupplied by the air chamber caused by rotation of fan blades. Air produced blows off dirt particles found in the sieve plate and dust particles found the beans collector vessel. Fine beans are then channelled to the receiving vessel. 3.2. Performance test The shelling machine was subjected to test and it was discovered to shelling beans very effectively having negligible losses and breakages. The estimated capacity of the machine is about was 630.32 kg/h. The efficiency of the machine was calculated from the Eq. (8) below to be equal to 92.7%. Efficiency= ((𝑊 1 − 𝑊 2 )/𝑊 1 )100 (8) Where 𝑊 1 is the weight of unshelling beans W 2 is the weight of beans shelling beans. 4 Conclusions The beans shelling machine fabricated shall peel harvested beans from our farms rapidly without any effect to the economy. This machine uses both man power and electricity power supply of 220volts at its standards. Skilled personnel are not needed in operating this machine because its parts are made easy to be operated upon by all farmers. Equally, its parts are made easy Such that when damaged or wear, it can be maintain. Moreover, it is cost efficient and its value is absolutely enjoyable. No radioactive gas emission or associated to its functionality. Uses the beating system which can easily be understood by all farmers since it is an improvement from hand beating. Declarations Acknowledgements This is not applicable Author contributions Noutegomo Boris: Conceptualization, Methodology, Investigation, Data curation, Formal analysis, Writing—Review & Editing, Supervision. Neh Sandra Fongeh : Software, Validation, Formal analysis, Writing—Original Draft Beching Roland Oru : Conceptualization, Methodology, Review & Editing. Funding This is not applicable. Data availability The data that support the findings of this study are openly available Competing interests The authors declared that there is no conflict of interest. Ethics approval and consent to participate This is not applicable. Consent for publication This is not applicable. References Hummel M, Hallahan BF, Brychkova G, Ramirez-Villegas J, Guwela V, Chataika B, Curley E, McKeown PC, Morrison L, Talsma EF, Beebe S, Jarvis A, Chirwa R, Spillane C. Reduction in nutritional quality and growing area suitability of common bean under climate change induced drought stress in Africa. 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J Food Process Preserv. 2019;43(5):13912. Suarez RM, Espinoza JC. Mechanical properties of bean pods and their implications for peeling design. Trans ASABE. 2018;61(2):729–36. Gonzalez FP, Morales DL. Evaluation of bean peeling efficiency using machine vision techniques. Food Bioprocess Technol. 2019;12(5):882–91. Sanchez MV, Gutierrez PX. Development of an automated bean peeling machine with integrated quality control. Food Bioprocess Technol. 2018;11(6):1207–19. Additional Declarations No competing interests reported. Cite Share Download PDF Status: Posted Version 1 posted You are reading this latest preprint version Research Square lets you share your work early, gain feedback from the community, and start making changes to your manuscript prior to peer review in a journal. As a division of Research Square Company, we’re committed to making research communication faster, fairer, and more useful. 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Also discoverable on Platform About Our Team In Review Editorial Policies Advisory Board Help Center Resources Author Services Accessibility API Access RSS feed Manage Cookie Preferences © Research Square 2026 | ISSN 2693-5015 (online) Privacy Policy Terms of Service Do Not Sell My Personal Information {"props":{"pageProps":{"initialData":{"identity":"rs-8729397","acceptedTermsAndConditions":true,"allowDirectSubmit":true,"archivedVersions":[],"articleType":"Research Article","associatedPublications":[],"authors":[{"id":598114034,"identity":"61f1efae-8d15-4b9f-9bd8-70163d0268f2","order_by":0,"name":"noutegomo 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shaft\u003c/p\u003e","description":"","filename":"floatimage3.png","url":"https://assets-eu.researchsquare.com/files/rs-8729397/v1/e6cae9c83bd1772c23548ba9.png"},{"id":103751153,"identity":"06af3720-0cfe-47d2-b822-c85bc25fdd23","added_by":"auto","created_at":"2026-03-02 13:03:02","extension":"png","order_by":4,"title":"Figure 4","display":"","copyAsset":false,"role":"figure","size":14870,"visible":true,"origin":"","legend":"\u003cp\u003eRepresentation of forces to be calculated.\u003c/p\u003e","description":"","filename":"floatimage4.png","url":"https://assets-eu.researchsquare.com/files/rs-8729397/v1/4507f06b284bc5ef1e27a035.png"},{"id":103751152,"identity":"3aee7eb7-7fc9-4d40-8a3e-53fc8c7f60cf","added_by":"auto","created_at":"2026-03-02 13:03:02","extension":"png","order_by":5,"title":"Figure 5","display":"","copyAsset":false,"role":"figure","size":10986,"visible":true,"origin":"","legend":"\u003cp\u003eVertical loading diagram.\u003c/p\u003e","description":"","filename":"floatimage5.png","url":"https://assets-eu.researchsquare.com/files/rs-8729397/v1/9ca63b5a920b3bb2bafbce36.png"},{"id":103751155,"identity":"69facb45-8f06-432e-be08-a876f095781c","added_by":"auto","created_at":"2026-03-02 13:03:02","extension":"png","order_by":6,"title":"Figure 6","display":"","copyAsset":false,"role":"figure","size":26286,"visible":true,"origin":"","legend":"\u003cp\u003eVertical bending moment diagram.\u003c/p\u003e","description":"","filename":"floatimage6.png","url":"https://assets-eu.researchsquare.com/files/rs-8729397/v1/2d223b545dfad0420546fee8.png"},{"id":103751159,"identity":"24002d3f-6087-49cc-9f3b-7c0283fc56cb","added_by":"auto","created_at":"2026-03-02 13:03:02","extension":"png","order_by":7,"title":"Figure 7","display":"","copyAsset":false,"role":"figure","size":13803,"visible":true,"origin":"","legend":"\u003cp\u003eHorizontal loading\u003c/p\u003e","description":"","filename":"floatimage7.png","url":"https://assets-eu.researchsquare.com/files/rs-8729397/v1/a5629070806a247bc2a61dc5.png"},{"id":103751156,"identity":"6c839629-4c7e-4f11-92a1-36cca5645385","added_by":"auto","created_at":"2026-03-02 13:03:02","extension":"png","order_by":8,"title":"Figure 8","display":"","copyAsset":false,"role":"figure","size":15916,"visible":true,"origin":"","legend":"\u003cp\u003eHorizontal loading force diagram\u003c/p\u003e","description":"","filename":"floatimage8.png","url":"https://assets-eu.researchsquare.com/files/rs-8729397/v1/99768ee5731e380951c3ab55.png"},{"id":103751161,"identity":"d9b8a379-d30b-4f3a-9f24-19542a001cd5","added_by":"auto","created_at":"2026-03-02 13:03:03","extension":"png","order_by":9,"title":"Figure 9","display":"","copyAsset":false,"role":"figure","size":31687,"visible":true,"origin":"","legend":"\u003cp\u003eHorizontal bending moment diagram.\u003c/p\u003e","description":"","filename":"floatimage9.png","url":"https://assets-eu.researchsquare.com/files/rs-8729397/v1/9182d925b154fade20fa6e1b.png"},{"id":104400241,"identity":"8fbf1cbd-eec0-49df-beb2-d8c2c669d901","added_by":"auto","created_at":"2026-03-11 12:09:19","extension":"png","order_by":10,"title":"Figure 10","display":"","copyAsset":false,"role":"figure","size":16612,"visible":true,"origin":"","legend":"\u003cp\u003eShelling mechanism.\u003c/p\u003e","description":"","filename":"floatimage10.png","url":"https://assets-eu.researchsquare.com/files/rs-8729397/v1/0a83ae0077b3c4391d64bc2e.png"},{"id":103751162,"identity":"cae508f1-50bd-429a-bd81-ac0b826ca668","added_by":"auto","created_at":"2026-03-02 13:03:03","extension":"png","order_by":11,"title":"Figure 11","display":"","copyAsset":false,"role":"figure","size":54737,"visible":true,"origin":"","legend":"\u003cp\u003epulleys-belt system.\u003c/p\u003e","description":"","filename":"floatimage11.png","url":"https://assets-eu.researchsquare.com/files/rs-8729397/v1/75c489d4470c904e57da72da.png"},{"id":104400632,"identity":"e1ee3556-cb02-4cda-8f32-23649387e809","added_by":"auto","created_at":"2026-03-11 12:10:33","extension":"png","order_by":12,"title":"Figure 12","display":"","copyAsset":false,"role":"figure","size":380962,"visible":true,"origin":"","legend":"\u003cp\u003eBeans shelling machine realised.\u003c/p\u003e","description":"","filename":"floatimage12.png","url":"https://assets-eu.researchsquare.com/files/rs-8729397/v1/f614f74bc8a8661aec9f6dcd.png"},{"id":105811328,"identity":"0f370f59-2db8-408d-af9b-6975b6b0aad4","added_by":"auto","created_at":"2026-03-31 11:26:59","extension":"pdf","order_by":0,"title":"","display":"","copyAsset":false,"role":"manuscript-pdf","size":2055957,"visible":true,"origin":"","legend":"","description":"","filename":"manuscript.pdf","url":"https://assets-eu.researchsquare.com/files/rs-8729397/v1/b27c3990-8165-4c8a-9096-e2eaaf50b825.pdf"}],"financialInterests":"No competing interests reported.","formattedTitle":"Design and realisation of a motorized beans shelling machine","fulltext":[{"header":"1. Introduction","content":"\u003cp\u003eCommon beans (\u003cem\u003ePhaseolus vulgaris\u003c/em\u003e L.) are a major food and income source in many developing regions. Their high nutritional value\u0026mdash;consisting of proteins, minerals, vitamins, and dietary fibre\u0026mdash;makes them a key component of diets in sub-Saharan Africa. In Cameroon, bean cultivation has expanded considerably, positioning the country as the seventh-largest producer in the region. National production rose from approximately 365,295 metric tons in 2017 to 373,624 metric tons in 2021, driven largely by population growth and increasing urban demand. However, this rise in production has not translated into lower market prices, largely due to persistent constraints in the production and post-harvest chain. These challenges include limited access to improved seed varieties, outdated farming tools, declining soil fertility, inadequate pest control, and substantial post-harvest losses. Manual shelling remains one of the most labor-intensive bottlenecks, contributing significantly to inefficiencies in the value chain.\u003c/p\u003e \u003cp\u003eThe introduction of agricultural machinery has been widely recognized as a means to improve efficiency and product quality. Olaoye [\u003cspan citationid=\"CR8\" class=\"CitationRef\"\u003e8\u003c/span\u003e] highlighted that although mechanical shelling technologies may involve high initial investment, they reduce labor intensity, maintain kernel quality, and minimize losses compared with traditional methods. This has encouraged several research efforts aimed at developing cost-effective shelling machines, particularly using locally available materials.\u003c/p\u003e \u003cp\u003eUnuigbe et al. [\u003cspan citationid=\"CR9\" class=\"CitationRef\"\u003e9\u003c/span\u003e] designed and constructed a bean sheller using local materials, supported by detailed component design and fabrication drawings. Their machine achieved a shelling efficiency of 81.3% with a processing capacity of 100 kg/h, demonstrating the feasibility of low-cost mechanical solutions. Ilori et al. [\u003cspan citationid=\"CR10\" class=\"CitationRef\"\u003e10\u003c/span\u003e] investigated ergonomic factors in hand-operated shellers, identifying that operator characteristics such as age, weight, and arm length significantly influence shelling efficiency, an important consideration for manually powered devices.\u003c/p\u003e \u003cp\u003eOther studies have focused on optimizing machine design for higher performance. Ashwin and Shaik [\u003cspan citationid=\"CR11\" class=\"CitationRef\"\u003e11\u003c/span\u003e] developed a hand-operated cylinder\u0026ndash;concave sheller that reached a shelling efficiency of 99.56% at 12% moisture content and 130 kg/h feed rate, with minimal unshelled grains and acceptable grain damage. Engineers at the USDA [\u003cspan citationid=\"CR12\" class=\"CitationRef\"\u003e12\u003c/span\u003e] designed an experimental gentle-handling sheller, which performed well at 15% moisture content but suffered from issues related to belt durability, low throughput, and reduced efficiency at higher moisture levels. Fox [\u003cspan citationid=\"CR13\" class=\"CitationRef\"\u003e13\u003c/span\u003e] proposed a rubber-roller sheller based on rolling and squeezing principles; however, it faced feeding limitations and did not perform satisfactorily on unhusked pods. Research on similar post-harvest processes provides useful insight into efficiency gains from mechanization. Karthickumar et al. [\u003cspan citationid=\"CR14\" class=\"CitationRef\"\u003e14\u003c/span\u003e] developed a continuous tamarind deseeding machine with a throughput of 75 kg/h and a maximum efficiency of 89.15%, reducing both cost and processing time relative to manual methods. Similarly, Hiregoudar and Udhayakumar [\u003cspan citationid=\"CR15\" class=\"CitationRef\"\u003e15\u003c/span\u003e] found that mechanical deseeding significantly increases output compared with traditional techniques, although at the cost of higher mechanical damage.\u003c/p\u003e \u003cp\u003eAdditional studies by Aluko [\u003cspan citationid=\"CR16\" class=\"CitationRef\"\u003e16\u003c/span\u003e], Babatunde et al. [\u003cspan citationid=\"CR17\" class=\"CitationRef\"\u003e17\u003c/span\u003e], and Uadia and Ogbu [\u003cspan citationid=\"CR18\" class=\"CitationRef\"\u003e18\u003c/span\u003e] focused on the design, fabrication, and evaluation of bean shelling machines with the aim of improving shelling efficiency, reducing processing time, and minimizing losses. These works collectively emphasize methodologies for machine design and the potential benefits of mechanization in bean processing. A review of the literature shows that while many prototypes have been developed, several challenges persist: Low shelling efficiency in early designs, Limited processing capacity, restricting commercial use, High levels of grain damage, often linked to bean size variability, Mechanical limitations, such as poor feeding systems or fragile components, Lack of standardization, with many machines remaining at prototype stage.\u003c/p\u003e \u003cp\u003eGiven these limitations, there is a clear need for a more efficient, robust, and commercially viable bean shelling machine adapted to local conditions. The current study responds to this need by designing and developing a locally fabricated sheller capable of improving throughput, reducing mechanical damage, and supporting wider adoption of mechanized post-harvest technologies.\u003c/p\u003e"},{"header":"2. Materials and method.","content":"\u003cdiv id=\"Sec3\" class=\"Section2\"\u003e \u003ch2\u003e2.1 Design Consideration\u003c/h2\u003e \u003cp\u003eThe design and development of a bean shelling machine must consider several important factors, including product quality, material selection, and process efficiency. Product quality is evaluated based on the preservation of the beans\u0026rsquo; physical and chemical properties. The construction materials should be resistant to corrosion, wear, and tear, while also being strong, readily available, and affordable. Other key considerations include the machine\u0026rsquo;s structural stability, ensuring it remains rigid during operation, and its ability to sort, meaning the separation of shelled beans into uniform aggregates within the shelling chamber. Affordability is also crucial, enabling farmers to compare the machine\u0026rsquo;s investment and maintenance costs with those of imported alternatives.\u003c/p\u003e \u003c/div\u003e \u003cdiv id=\"Sec4\" class=\"Section2\"\u003e \u003ch2\u003e2.2. Conceptual design\u003c/h2\u003e \u003cp\u003eAutoCAD software was used to design components and to assembly them for the geometrical model of the machine. It was also used to simulate the rigidity of the frame in other to choose the suitable materials that could withstand the loads and preserve the stability. Figures\u0026nbsp;1and 2 show respectively the exploded and isomeric views of the machine designed.\u003c/p\u003e \u003cp\u003e \u003c/p\u003e \u003cp\u003e \u003c/p\u003e \u003c/div\u003e \u003cdiv id=\"Sec5\" class=\"Section2\"\u003e \u003ch2\u003e2.3. Design analysis and calculations\u003c/h2\u003e \u003cp\u003eThe design of various component parts of shelling machine is governed by physical, mechanical and engineering properties of beans. Others are the mechanism of rotating shaft over the concave at a specific clearance for the downward movement of the shelled grains. We are going to present the design analysis and calculations for major component parts.\u003c/p\u003e \u003cdiv id=\"Sec6\" class=\"Section3\"\u003e \u003ch2\u003e2.3.1. Frame\u003c/h2\u003e \u003cp\u003eThe two primary factors considered in selecting the frame material were weight and strength, as the frame would be subjected to compressive forces and torque. In this study, a hollow square steel tube (S235JR, 16 mm \u0026times; 5 mm) was used to provide the necessary rigidity. The frame components were fabricated through cutting with an angle grinder, and the assembly was completed using the MIG/MAG welding process.\u003c/p\u003e \u003c/div\u003e \u003cdiv id=\"Sec7\" class=\"Section3\"\u003e \u003ch2\u003e2.3.2. Hopper\u003c/h2\u003e \u003cp\u003eThe hopper is designed to be fed in a horizontal position only. The material used for the construction is carbon steel S235 JR 2000x 1000 sheet metal, which is readily available in the market and relatively affordable.\u003c/p\u003e \u003c/div\u003e \u003cdiv id=\"Sec8\" class=\"Section3\"\u003e \u003ch2\u003e2.3.3. Beans inlet vessel\u003c/h2\u003e \u003cp\u003eIt was done by carbon steel S235 JR 2000x 1000 Cutting via a shearing machine and Bending via an angle bending machine with the dimensions of 470mm x 285.69mm.\u003c/p\u003e \u003c/div\u003e \u003cdiv id=\"Sec9\" class=\"Section3\"\u003e \u003ch2\u003e2.3.4.. Sieve chamber connected to mechanism\u003c/h2\u003e \u003cp\u003eIt has the dimensions of 850mm x 360mm realized with carbon steel by cutting using the shearing machine.\u003c/p\u003e \u003c/div\u003e \u003cdiv id=\"Sec10\" class=\"Section3\"\u003e \u003ch2\u003e2.3.5. Blower\u003c/h2\u003e \u003cp\u003eIt is the composition of the fan system with fan blades of 500mm x100mm enclosed in the shaft realized by Cutting/Cleaning and the Air chamber of 767mm x 200mm, Radius 80mm realized with cutting, Rolling and Welding process.\u003c/p\u003e \u003c/div\u003e \u003cdiv id=\"Sec11\" class=\"Section3\"\u003e \u003ch2\u003e2.3.6. Design of shaft\u003c/h2\u003e \u003cp\u003eIt is a cylindrical solid rod for transmitting motion through a set of load carried on it. The design is based on fluctuating torque, bending moment and shearing force.\u003c/p\u003e \u003cp\u003e \u003cul\u003e \u003cli\u003e \u003cp\u003eDetermination of Maximum Bending Moment \u0026#119872;\u0026#119887;\u003c/p\u003e \u003c/li\u003e \u003c/ul\u003e \u003c/p\u003e \u003cp\u003eThe maximum bending moment is given by Eq.\u0026nbsp;(\u003cspan refid=\"Equ1\" class=\"InternalRef\"\u003e1\u003c/span\u003e)\u003cdiv id=\"Equ1\" class=\"Equation\"\u003e\u003cdiv format=\"TEX\" class=\"mathdisplay\" id=\"FileID_Equ1\" name=\"EquationSource\"\u003e\n$$\\:Mb=\\sqrt{{\\left(\\text{M}\\text{B}\\text{V}\\right)}^{2}-{\\left(\\text{M}\\text{B}\\text{H}\\right)}^{2}}$$\u003c/div\u003e\u003cdiv class=\"EquationNumber\"\u003e1\u003c/div\u003e\u003c/div\u003e\u003c/p\u003e \u003cp\u003eWhere \u0026#119872;\u0026#119861;\u0026#119881; is the vertical bending moment (Nm).and \u0026#119872;\u0026#119861;\u0026#119867; the horizontal bending moment (Nm). Figure\u0026nbsp;\u003cspan refid=\"Fig3\" class=\"InternalRef\"\u003e3\u003c/span\u003e bellow presents the different loads acting on the shaft. W represents the centrifugal force of the pulley, q is the uniformly distributed loads in housing chamber due to weight of beans and R\u003csub\u003eA\u003c/sub\u003e, R\u003csub\u003eB\u003c/sub\u003e are reactions of the bearings. Figure\u0026nbsp;\u003cspan refid=\"Fig4\" class=\"InternalRef\"\u003e4\u003c/span\u003e presents forces acting on the shaft to be calculated.\u003c/p\u003e \u003cp\u003e \u003c/p\u003e \u003cp\u003e \u003c/p\u003e \u003cp\u003eCalculations:\u003c/p\u003e \u003cp\u003eWeight of pulley W= 1kg \u0026#119865;\u003csub\u003e\u0026#119862;\u003c/sub\u003e = 1kg x 10\u0026thinsp;=\u0026thinsp;10N\u003c/p\u003e \u003cp\u003eWeight of beans M= \u0026#120588;\u0026#119881; = \u0026#120587;\u0026#119863;\u003csup\u003e2\u003c/sup\u003e\u0026#119871;\u0026#120588; =3.14 x 0.32 \u0026#119909; 1 \u0026#119909; 24\u0026thinsp;=\u0026thinsp;6.7kg \u0026#119865;\u003csub\u003e\u0026#119863;\u003c/sub\u003e = 6.7kg x 10 = 67N\u003c/p\u003e \u003cp\u003eTaking moment about R\u003csub\u003eA\u003c/sub\u003e: -10N x 0.25m -R\u003csub\u003eB\u003c/sub\u003e x 1m\u0026thinsp;+\u0026thinsp;67N x 0.5m\u0026thinsp;=\u0026thinsp;0 -2.5- RB\u0026thinsp;+\u0026thinsp;33.5\u0026thinsp;=\u0026thinsp;0\u003c/p\u003e \u003cp\u003eR\u003csub\u003eB\u003c/sub\u003e= 31N\u003c/p\u003e \u003cp\u003eR\u003csub\u003eA\u003c/sub\u003e=46N\u003c/p\u003e \u003cp\u003eFigure \u003cspan refid=\"Fig5\" class=\"InternalRef\"\u003e5\u003c/span\u003e presents the vertical loading diagram\u003c/p\u003e \u003cp\u003e \u003c/p\u003e \u003cp\u003eAt C, MBV\u0026thinsp;=\u0026thinsp;0\u003c/p\u003e \u003cp\u003eAt A, when x\u0026thinsp;=\u0026thinsp;0.25 m MBV\u0026thinsp;=\u0026thinsp;10 x 0.25\u0026thinsp;=\u0026thinsp;2.5Nm\u003c/p\u003e \u003cp\u003eAt D, when x\u0026thinsp;=\u0026thinsp;0.75 m MBV = (10 x 0.75) \u0026ndash; (46 x 0.5) MBV\u0026thinsp;=\u0026thinsp;\u0026minus;\u0026thinsp;15.5Nm\u003c/p\u003e \u003cp\u003eFigure \u003cspan refid=\"Fig6\" class=\"InternalRef\"\u003e6\u003c/span\u003e presents vertical bending moment diagram.\u003c/p\u003e \u003cp\u003e \u003c/p\u003e \u003cp\u003eCalculations of horizontal bending moment\u003c/p\u003e \u003cp\u003eFigure \u003cspan refid=\"Fig7\" class=\"InternalRef\"\u003e7\u003c/span\u003e presents the Horizontal loading.\u003c/p\u003e \u003cp\u003e \u003c/p\u003e \u003cp\u003eFrom Fig.\u0026nbsp;\u003cspan refid=\"Fig7\" class=\"InternalRef\"\u003e7\u003c/span\u003e, taking moment about R\u003csub\u003eB\u003c/sub\u003e:\u003c/p\u003e \u003cp\u003e0\u0026thinsp;=\u0026thinsp;10N x 0.25m\u0026thinsp;+\u0026thinsp;R\u003csub\u003eC\u003c/sub\u003e x 1m; 0\u0026thinsp;=\u0026thinsp;2.5\u0026thinsp;+\u0026thinsp;R\u003csub\u003eC\u003c/sub\u003e R\u003csub\u003eC\u003c/sub\u003e\u0026thinsp;=\u0026thinsp;\u0026minus;\u0026thinsp;2.5N\u003c/p\u003e \u003cp\u003eR\u003csub\u003eB\u003c/sub\u003e + R\u003csub\u003eC\u003c/sub\u003e = 10N, R\u003csub\u003eB\u003c/sub\u003e = 12.5 N\u003c/p\u003e \u003cp\u003eFigures \u003cspan refid=\"Fig8\" class=\"InternalRef\"\u003e8\u003c/span\u003e and \u003cspan refid=\"Fig9\" class=\"InternalRef\"\u003e9\u003c/span\u003e present horizontal loading force diagram and horizontal bending moment diagram respectively.\u003c/p\u003e \u003cp\u003e \u003c/p\u003e \u003cp\u003eAt A, MBH\u0026thinsp;=\u0026thinsp;0\u003c/p\u003e \u003cp\u003eAt B, when x\u0026thinsp;=\u0026thinsp;0.23 m MBH\u0026thinsp;=\u0026thinsp;10 x 0.25\u0026thinsp;=\u0026thinsp;2.5Nm\u003c/p\u003e \u003cp\u003eAt C, when x\u0026thinsp;=\u0026thinsp;1.25 m MBH = (10 x 1.25) \u0026ndash; (12.5 x 1) MBH\u0026thinsp;=\u0026thinsp;0 Nm\u003c/p\u003e \u003cp\u003e \u003c/p\u003e \u003cp\u003eTherefore the maximum bending moment is:\u003c/p\u003e \u003cp\u003e \u003cem\u003eM\u0026#119887;\u003c/em\u003e=\u003cspan class=\"InlineEquation\"\u003e\u003cspan class=\"mathinline\"\u003e\\(\\:\\sqrt{{\\left(15.5\\right)}^{2}-{\\left(2.5\\right)}^{2}}\\)\u003c/span\u003e\u003c/span\u003e =15.70 Nm\u003c/p\u003e \u003cp\u003e \u003cul\u003e \u003cli\u003e \u003cp\u003eDetermination of Torsional Moment, Mt\u003c/p\u003e \u003c/li\u003e \u003c/ul\u003e \u003c/p\u003e \u003cp\u003eThe torsional moment, Mt is given by\u003c/p\u003e \u003cp\u003eMt\u0026thinsp;=\u0026thinsp;F\u003csub\u003eD\u003c/sub\u003e x r where r is the length of the sprike tooth linked on the shaft by welding process and constitute shelling mechanism. The diagram is presented on Fig.\u0026nbsp;\u003cspan refid=\"Fig10\" class=\"InternalRef\"\u003e10\u003c/span\u003e bellow.\u003c/p\u003e \u003cp\u003e \u003c/p\u003e \u003cp\u003eMt\u0026thinsp;=\u0026thinsp;6.7 x 0.2\u0026thinsp;=\u0026thinsp;1,34N.m\u003c/p\u003e \u003cp\u003e\u0026bull; Determination of shaft diameter\u003c/p\u003e \u003cp\u003eFor proper designing there is need to determine the shaft diameter, Eq.\u0026nbsp;(\u003cspan refid=\"Equ2\" class=\"InternalRef\"\u003e2\u003c/span\u003e) was adopted:\u003cdiv id=\"Equ2\" class=\"Equation\"\u003e\u003cdiv format=\"TEX\" class=\"mathdisplay\" id=\"FileID_Equ2\" name=\"EquationSource\"\u003e\n$$\\:{d}^{3}=\\frac{16}{\\pi\\:\\delta\\:s}{\\left[{\\left({K}_{b}{M}_{b}\\right)}^{2}+{\\left({K}_{t}{M}_{t}\\right)}^{2}\\right]}^{\\frac{1}{2}}$$\u003c/div\u003e\u003cdiv class=\"EquationNumber\"\u003e2\u003c/div\u003e\u003c/div\u003e\u003c/p\u003e \u003cp\u003ewhere d is diameter of shaft (mm), K\u003csub\u003eb\u003c/sub\u003e are bending moment fatigue and shock, K\u003csub\u003et\u003c/sub\u003e are fatigue and combined factor for torsional moment, M\u003csub\u003eb\u003c/sub\u003e are resultant bending moment (Nm), Mt are resultant torsional moment (Nm), δsy are allowable bending stress (MN m\u003csup\u003e\u0026minus;\u0026thinsp;2\u003c/sup\u003e).\u003c/p\u003e \u003cp\u003e \u003cstrong\u003eAssumptions\u003c/strong\u003e \u003cp\u003eδs\u0026thinsp;=\u0026thinsp;47 x 10\u003csup\u003e6\u003c/sup\u003e N/m K\u003csub\u003et\u003c/sub\u003e=K\u003csub\u003eb\u003c/sub\u003e=1.5\u003cdiv id=\"Equa\" class=\"Equation\"\u003e\u003cdiv format=\"TEX\" class=\"mathdisplay\" id=\"FileID_Equa\" name=\"EquationSource\"\u003e\n$$\\:{d}^{3}=\\frac{16}{47\\:\\text{x}\\:106\\:\\pi\\:}{\\left[{\\left(1.5\\text{x}15.7\\:\\right)}^{2}+{\\left(\\:1.5\\text{x}1.34\\right)}^{2}\\right]}^{\\frac{1}{2}}$$\u003c/div\u003e\u003c/div\u003e\u003c/p\u003e \u003c/p\u003e \u003cp\u003ed\u0026thinsp;=\u0026thinsp;0.01644m\u003c/p\u003e \u003cp\u003eWe should choice a diameter of 20mm\u003c/p\u003e \u003c/div\u003e \u003cdiv id=\"Sec12\" class=\"Section3\"\u003e \u003ch2\u003e2.3.7. Materials selection\u003c/h2\u003e \u003cp\u003e\u0026bull; Power requirement of motorized beans Shelling. The Power P (W) requirement was calculated based on the motor and belt efficiency of 70% and 75% respectively using Eq.\u0026nbsp;(3).\u003c/p\u003e \u003cp\u003eP= \u003cspan class=\"InlineEquation\"\u003e\u003cspan class=\"mathinline\"\u003e\\(\\:\\frac{\\text{P}{\\prime\\:}}{\\text{m}\\text{o}\\text{t}\\text{o}\\text{r}\\:\\text{e}\\text{f}\\text{f}\\text{i}\\text{c}\\text{i}\\text{e}\\text{n}\\text{c}\\text{y}\\:\\text{x}\\:\\text{b}\\text{e}\\text{l}\\text{t}\\:\\text{e}\\text{f}\\text{f}\\text{i}\\text{c}\\text{i}\\text{e}\\text{n}\\text{c}\\text{y}\\:}\\text{x}\\:\\text{s}\\text{a}\\text{f}\\text{e}\\text{t}\\text{y}\\:\\text{f}\\text{a}\\text{c}\\text{t}\\text{o}\\text{r}\\:\\)\u003c/span\u003e\u003c/span\u003e (3)\u003c/p\u003e \u003cp\u003eWhere P\u0026rsquo; is the theorical power (W)\u003c/p\u003e \u003cp\u003eP\u0026rsquo;= F \u0026times; V\u003c/p\u003e \u003cp\u003eWhere F is force of shelling (N), V are velocity (m/s).\u003c/p\u003e \u003cp\u003eV = \u0026#120587;DN\u003c/p\u003e \u003cp\u003eAccording to [\u003cspan citationid=\"CR17\" class=\"CitationRef\"\u003e17\u003c/span\u003e], the shelling speed that will give very low mechanical damage, but high threshing output is within the range of 950 revolutions per minute.\u003c/p\u003e \u003cp\u003eLet\u0026rsquo;s us take N\u0026thinsp;=\u0026thinsp;950 rpm and safety factor equal to 2\u003c/p\u003e \u003cp\u003eP\u0026rsquo;= 15.5 \u0026times; 3.14 x 0.4 x 950/60\u0026thinsp;=\u0026thinsp;368W\u003c/p\u003e \u003cp\u003eP= \u003cspan class=\"InlineEquation\"\u003e\u003cspan class=\"mathinline\"\u003e\\(\\:\\frac{368}{70\\text{%}\\:\\text{x}\\:75\\text{%}}\\:\\:\\times\\:2\\)\u003c/span\u003e\u003c/span\u003e\u003c/p\u003e \u003cp\u003eP= 1400W\u003c/p\u003e \u003cp\u003eThen the motor power should be around 2HP since 1HP=737W\u003c/p\u003e \u003cp\u003e\u0026bull; Determination of the diameter of the driven pulley\u003c/p\u003e \u003cp\u003eTo calculate the diameter D of the driven pulley we use the Fig.\u0026nbsp;11 representing the pulleys-belt system. The Eq.\u0026nbsp;(5) presents the relationship between the diameters and rpm of the two pulleys.\u003c/p\u003e \u003cp\u003e \u003c/p\u003e \u003cp\u003eN\u003csub\u003e1\u003c/sub\u003e d\u0026thinsp;=\u0026thinsp;N\u003csub\u003e2\u003c/sub\u003e D (5)\u003c/p\u003e \u003cp\u003eN\u003csub\u003e1\u003c/sub\u003e speed of driver=1400rpm and N\u003csub\u003e2\u003c/sub\u003e speed of driven\u003c/p\u003e \u003cp\u003eD diameter of \u003cspan class=\"InlineEquation\"\u003e\u003cspan class=\"mathinline\"\u003e\\(\\:d\\)\u003c/span\u003e\u003c/span\u003eriven and d diameter of driver=140mm\u003c/p\u003e \u003cp\u003e \u003cspan class=\"InlineEquation\"\u003e \u003cspan class=\"mathinline\"\u003e\\(\\:D=\\frac{{N}_{1}d}{{N}_{2}}\\:=\\:\\frac{1400\\text{X}140}{850}\\:=\\:\\)\u003c/span\u003e \u003c/span\u003e206\u003c/p\u003e \u003cp\u003eD\u0026thinsp;=\u0026thinsp;206 mm\u003c/p\u003e \u003c/div\u003e \u003cdiv id=\"Sec13\" class=\"Section3\"\u003e \u003ch2\u003e2.4.1. V-belt selection\u003c/h2\u003e \u003cp\u003e \u003cul\u003e \u003cli\u003e \u003cp\u003eLength of belt\u003c/p\u003e \u003c/li\u003e \u003c/ul\u003e \u003c/p\u003e \u003cp\u003eFor a motor rating of 0.7W, the suitable choice is class A with a pitch length of 1.06mm according to IS: 2494\u0026ndash;1974 standard. Top width of 13mm. we choice a standard length of 925 mm.\u003c/p\u003e \u003cp\u003e \u003cul\u003e \u003cli\u003e \u003cp\u003eCentre Distance of Belt\u003c/p\u003e \u003c/li\u003e \u003c/ul\u003e \u003c/p\u003e \u003cp\u003eThe length of the belt is given by the Eq.\u0026nbsp;(6);\u003c/p\u003e \u003cp\u003eL\u0026thinsp;=\u0026thinsp;2x + (π/2)(D\u0026thinsp;+\u0026thinsp;d) + (D \u0026ndash; d)\u003csup\u003e2/\u003c/sup\u003e(4x) (6)\u003c/p\u003e \u003cp\u003eWhere; L\u0026thinsp;=\u0026thinsp;length of belt, D and d are the diameter of the driven and driving pulleys respectively,\u003c/p\u003e \u003cp\u003ex\u0026thinsp;=\u0026thinsp;centre-to-centre distance between the driving and driven pulleys.\u003c/p\u003e \u003c/div\u003e \u003c/div\u003e\n\u003ch3\u003e925 = 2x + (π/2)(206 + 130) + (206–130)2/(4x)\u003c/h3\u003e\n\u003cp\u003ex\u0026thinsp;=\u0026thinsp;200mm\u003c/p\u003e \u003cp\u003eThe power transmitted by belt is given by Eq.\u0026nbsp;(7)\u003c/p\u003e \u003cp\u003eP = (T1 \u0026ndash; T2)V (7)\u003c/p\u003e \u003cp\u003eV = (πDN)/60. Also,\u003c/p\u003e \u003cp\u003eT\u003csub\u003e1\u003c/sub\u003e/T\u003csub\u003e2\u003c/sub\u003e\u0026thinsp;=\u0026thinsp;exp(\u0026micro;θ cosec β),\u003c/p\u003e \u003cp\u003ewhere:\u003c/p\u003e \u003cp\u003eβ\u0026thinsp;=\u0026thinsp;groove semi-angle 2β\u0026thinsp;=\u0026thinsp;34;\u003c/p\u003e \u003cp\u003eθ\u0026thinsp;=\u0026thinsp;angle of lap;\u003c/p\u003e \u003cp\u003eα\u0026thinsp;=\u0026thinsp;angle of contact at the smaller pulley;\u003c/p\u003e \u003cp\u003e\u0026micro;\u0026thinsp;=\u0026thinsp;coefficient of friction.\u003c/p\u003e \u003cp\u003eThe coefficient of friction for rubber belt on cast iron or steel operating on dry surface is \u0026micro;\u0026thinsp;=\u0026thinsp;0.3. The angle of lap for open V-belt drive is given as:\u003c/p\u003e \u003cp\u003ex\u0026thinsp;=\u0026thinsp;distance between pulleys;\u003c/p\u003e \u003cp\u003ed\u0026thinsp;=\u0026thinsp;diameter of smaller pulley;\u003c/p\u003e \u003cp\u003eD\u0026thinsp;=\u0026thinsp;diameter of bigger pulley.\u003c/p\u003e \u003cp\u003eθ = (180\u0026ndash;18.4) x π/180\u0026thinsp;=\u0026thinsp;2.81rad\u003c/p\u003e \u003cp\u003eP\u0026thinsp;=\u0026thinsp;πDN (T\u003csub\u003e1\u003c/sub\u003e \u0026ndash; T\u003csub\u003e2\u003c/sub\u003e)/60 T\u003csub\u003e1\u003c/sub\u003e \u0026ndash; T\u003csub\u003e2\u003c/sub\u003e= \u003cspan class=\"InlineEquation\"\u003e\u003cspan class=\"mathinline\"\u003e\\(\\:\\frac{60\\text{X}1400}{3.14\\text{X}0.130\\text{x}1500}=137\\)\u003c/span\u003e\u003c/span\u003e\u003c/p\u003e \u003cp\u003eT\u003csub\u003e1\u003c/sub\u003e/T\u003csub\u003e2\u003c/sub\u003e = \u003cspan class=\"InlineEquation\"\u003e\u003cspan class=\"mathinline\"\u003e\\(\\:\\:\\)\u003c/span\u003e\u003c/span\u003eexp(0.3x2.81x cosec17)\u0026thinsp;=\u0026thinsp;2.2\u003c/p\u003e \u003cp\u003e \u003cspan class=\"InlineEquation\"\u003e \u003cspan class=\"mathinline\"\u003e\\(\\:\\frac{\\:{T}_{2+137}\\:}{{T}_{2}}\\)\u003c/span\u003e \u003c/span\u003e=2.2\u003c/p\u003e \u003cp\u003eT\u003csub\u003e2\u003c/sub\u003e=114N\u003c/p\u003e \u003cp\u003eT\u003csub\u003e1\u003c/sub\u003e=250N\u003c/p\u003e"},{"header":"3. Results and Discussions","content":"\u003cp\u003eFigure \u003cspan refid=\"Fig12\" class=\"InternalRef\"\u003e12\u003c/span\u003e is the beans shelling machine realised.\u003c/p\u003e \u003cp\u003e \u003c/p\u003e \u003cdiv id=\"Sec16\" class=\"Section2\"\u003e \u003ch2\u003e3.1. Working principle of the beans shelling machine\u003c/h2\u003e \u003cp\u003eUntreated beans is fed into the hopper then channels the beans to the hopper top cover through the shield box. The shield box prevents beans from pouring and therefore channels the beans to the rotor mechanism. The mechanism is made up of a shaft with square tubes welded on the surface of the shaft. This is the main part of the machine because this causes the force used in beating the beans. It is enclosed to the bottom hopper and a sieve vessel. The sieve vessel contains holes drilled at 10mm which serves as channel for the peeled beans to pass through. The bottom hopper contains an outlet where the peeled beans pass through. The peeled beans then fall on the sieve plate. The sieve plate is connected to the hopper bottom cover via connecting rod. The connecting rod is linked to the hopper bottom cover and the sieve plate via drilled holes of 10mm screwed properly to ensure stability. The stability of the plate is reinforced by sieve carrier below the sieve plate. As the peeled beans falls on the sieve plate, air issupplied by the air chamber caused by rotation of fan blades. Air produced blows off dirt particles found in the sieve plate and dust particles found the beans collector vessel. Fine beans are then channelled to the receiving vessel.\u003c/p\u003e \u003c/div\u003e \u003cdiv id=\"Sec17\" class=\"Section2\"\u003e \u003ch2\u003e3.2. Performance test\u003c/h2\u003e \u003cp\u003eThe shelling machine was subjected to test and it was discovered to shelling beans very effectively having negligible losses and breakages. The estimated capacity of the machine is about was 630.32 kg/h. The efficiency of the machine was calculated from the Eq.\u0026nbsp;(8) below to be equal to 92.7%.\u003c/p\u003e \u003cp\u003eEfficiency= ((\u0026#119882;\u003csub\u003e1\u003c/sub\u003e \u0026minus; \u0026#119882;\u003csub\u003e2\u003c/sub\u003e)/\u0026#119882;\u003csub\u003e1\u003c/sub\u003e)100 (8)\u003c/p\u003e \u003cp\u003eWhere \u0026#119882;\u003csub\u003e1\u003c/sub\u003e is the weight of unshelling beans\u003c/p\u003e \u003cp\u003eW\u003csub\u003e2\u003c/sub\u003e is the weight of beans shelling beans.\u003c/p\u003e \u003c/div\u003e"},{"header":"4 Conclusions","content":"\u003cp\u003eThe beans shelling machine fabricated shall peel harvested beans from our farms rapidly without any effect to the economy. This machine uses both man power and electricity power supply of 220volts at its standards. Skilled personnel are not needed in operating this machine because its parts are made easy to be operated upon by all farmers. Equally, its parts are made easy Such that when damaged or wear, it can be maintain. Moreover, it is cost efficient and its value is absolutely enjoyable. No radioactive gas emission or associated to its functionality. Uses the beating system which can easily be understood by all farmers since it is an improvement from hand beating.\u003c/p\u003e"},{"header":"Declarations","content":"\u003cp\u003e\u003cstrong\u003eAcknowledgements\u003c/strong\u003e\u003c/p\u003e\n\u003cp\u003eThis is not applicable\u003c/p\u003e\n\u003cp\u003e\u003cstrong\u003eAuthor contributions\u003c/strong\u003e\u003c/p\u003e\n\u003cp\u003e\u003cstrong\u003eNoutegomo Boris:\u0026nbsp;\u003c/strong\u003eConceptualization, Methodology, Investigation, Data curation, Formal analysis, Writing\u0026mdash;Review \u0026amp; Editing, Supervision.\u003c/p\u003e\n\u003cp\u003e\u003cstrong\u003eNeh Sandra Fongeh\u003c/strong\u003e\u0026nbsp; : Software, Validation, Formal analysis, Writing\u0026mdash;Original Draft\u003c/p\u003e\n\u003cp\u003e\u003cstrong\u003eBeching Roland Oru\u003c/strong\u003e : Conceptualization, Methodology, Review \u0026amp; Editing.\u003c/p\u003e\n\u003cp\u003e\u003cstrong\u003eFunding\u003c/strong\u003e\u003c/p\u003e\n\u003cp\u003eThis is not applicable.\u003c/p\u003e\n\u003cp\u003e\u003cstrong\u003eData availability\u003c/strong\u003e\u003c/p\u003e\n\u003cp\u003eThe data that support the findings of this study are openly available \u0026nbsp;\u003c/p\u003e\n\u003cp\u003e\u003cstrong\u003eCompeting interests\u003c/strong\u003e\u003c/p\u003e\n\u003cp\u003eThe authors declared that there is no conflict of interest.\u003c/p\u003e\n\u003cp\u003e\u003cstrong\u003eEthics approval and consent to participate\u003c/strong\u003e\u003c/p\u003e\n\u003cp\u003eThis is not applicable.\u003c/p\u003e\n\u003cp\u003e\u003cstrong\u003eConsent for publication\u003c/strong\u003e\u003c/p\u003e\n\u003cp\u003eThis is not applicable.\u003c/p\u003e"},{"header":"References","content":"\u003col\u003e\u003cli\u003e\u003cspan\u003eHummel M, Hallahan BF, Brychkova G, Ramirez-Villegas J, Guwela V, Chataika B, Curley E, McKeown PC, Morrison L, Talsma EF, Beebe S, Jarvis A, Chirwa R, Spillane C. 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Design, Fabrication and Performance Evaluation of a Bean Sheller. food J, 2012.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eFashina AB, Abdulahi H. Performance evaluation of a locally developed direct-power-take off driven maize thresher. J Agricultural Technol. 1994;2(1):1\u0026ndash;5.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eFernandez LM, Ramirez AB. Design and development of a lowcost automated bean peeling machine for smallholder farmers. J Food Eng. 2019;245:18\u0026ndash;26.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eFlores DR, Morales JC. Development of a solar-powered bean peeling machine for rural communities. Renewable Energy. 2021;163:1288\u0026ndash;300.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eCastillo MA, Diaz FT. Evaluation of different bean varieties for mechanical peeling efficiency. J Food Process Preserv. 2019;43(5):13912.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eSuarez RM, Espinoza JC. Mechanical properties of bean pods and their implications for peeling design. Trans ASABE. 2018;61(2):729\u0026ndash;36.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eGonzalez FP, Morales DL. Evaluation of bean peeling efficiency using machine vision techniques. Food Bioprocess Technol. 2019;12(5):882\u0026ndash;91.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eSanchez MV, Gutierrez PX. Development of an automated bean peeling machine with integrated quality control. Food Bioprocess Technol. 2018;11(6):1207\u0026ndash;19.\u003c/span\u003e\u003c/li\u003e\u003c/ol\u003e"}],"fulltextSource":"","fullText":"","funders":[],"hasAdminPriorityOnWorkflow":false,"hasManuscriptDocX":true,"hasOptedInToPreprint":true,"hasPassedJournalQc":"","hasAnyPriority":false,"hideJournal":true,"highlight":"","institution":"","isAcceptedByJournal":false,"isAuthorSuppliedPdf":false,"isDeskRejected":"","isHiddenFromSearch":false,"isInQc":false,"isInWorkflow":false,"isPdf":false,"isPdfUpToDate":true,"isWithdrawnOrRetracted":false,"journal":{"display":true,"email":"[email protected]","identity":"researchsquare","isNatureJournal":false,"hasQc":true,"allowDirectSubmit":true,"externalIdentity":"","sideBox":"","snPcode":"","submissionUrl":"/submission","title":"Research Square","twitterHandle":"researchsquare","acdcEnabled":true,"dfaEnabled":false,"editorialSystem":"","reportingPortfolio":"","inReviewEnabled":false,"inReviewRevisionsEnabled":true},"keywords":"design, realisation, beans, shelling machine","lastPublishedDoi":"10.21203/rs.3.rs-8729397/v1","lastPublishedDoiUrl":"https://doi.org/10.21203/rs.3.rs-8729397/v1","license":{"name":"CC BY 4.0","url":"https://creativecommons.org/licenses/by/4.0/"},"manuscriptAbstract":"\u003cp\u003eCommon beans (\u003cem\u003ePhaseolus vulgaris\u003c/em\u003e L.) are an essential staple crop widely grown across many developing nations. Recognizing the significant value and potential of this crop has led to the push for creating a mechanized bean shelling system as part of modern agricultural planning. This study focused on design and realisation of beans shelling machine. The machine was designed and realisation was achieved using appropriate engineering materials selected for various parts of the machine. This machine incorporated an air chamber system which was used in air production for waste disposal. Peeled beans was collected via a collecting vessel. Pulleys were used as speed reducers to transmit power and movement in order to enhance efficiency of the machine and the preservation of the good quality product. The machine performed well when it is motorised with a 2HP motor 1400rpm and a turning speed of 950rpm and average torque of 4.944Nm. Pulley groove selected at 206mm. we obtained for 92.7% beans peeling efficiency with a 630.32 kg/h of beans shelled.\u003c/p\u003e","manuscriptTitle":"Design and realisation of a motorized beans shelling machine","msid":"","msnumber":"","nonDraftVersions":[{"code":1,"date":"2026-03-02 13:02:48","doi":"10.21203/rs.3.rs-8729397/v1","editorialEvents":[{"type":"communityComments","content":0}],"status":"published","journal":{"display":true,"email":"[email protected]","identity":"researchsquare","isNatureJournal":false,"hasQc":true,"allowDirectSubmit":true,"externalIdentity":"","sideBox":"","snPcode":"","submissionUrl":"/submission","title":"Research Square","twitterHandle":"researchsquare","acdcEnabled":true,"dfaEnabled":false,"editorialSystem":"","reportingPortfolio":"","inReviewEnabled":false,"inReviewRevisionsEnabled":true}}],"origin":"","ownerIdentity":"d6b99935-7b97-4cfa-917e-291eeddf7b7a","owner":[],"postedDate":"March 2nd, 2026","published":true,"recentEditorialEvents":[],"rejectedJournal":[],"revision":"","amendment":"","status":"posted","subjectAreas":[],"tags":[],"updatedAt":"2026-03-31T11:26:36+00:00","versionOfRecord":[],"versionCreatedAt":"2026-03-02 13:02:48","video":"","vorDoi":"","vorDoiUrl":"","workflowStages":[]},"version":"v1","identity":"rs-8729397","journalConfig":"researchsquare"},"__N_SSP":true},"page":"/article/[identity]/[[...version]]","query":{"redirect":"/article/rs-8729397","identity":"rs-8729397","version":["v1"]},"buildId":"XKTyCvWXoU3ODBz1xrDgd","isFallback":false,"isExperimentalCompile":false,"dynamicIds":[84888],"gssp":true,"scriptLoader":[]}