Small walnut green seedcase removing and cleaning machine

Abstract

The utility model relates to the technical field of agricultural machining, in particular to a small walnut green seedcase removing and cleaning machine which comprises a rack, a peeling mechanism, a power mechanism and a cleaning mechanism. According to the green-husk walnut peeling machine, full-closed operation is adopted, and the stability and safety of the green-husk walnut peeling machine in the working process are improved. The peeling mode that the inner cylinder and the stirring blade rotate oppositely is adopted, meanwhile, the cleaning device is additionally arranged, and the peeling effect and the peeling efficiency are improved. Rapid peeling and deep cleaning of green-husk walnuts can be achieved, labor is saved, and the working efficiency is improved.

Description

TECHNICAL FIELD

[0001] The utility model relates to agricultural mechanical processing technical field, especially a small -size walnut green skin removes cleaning machine. BACKGROUND

[0002] Walnut is a nut enjoying global reputation, and is loved by people because of its rich nutritional value, excellent medical efficacy and wide industrial application. China, as one of the main walnut producing areas in the world, not only occupies a prominent position in yield, but also is an important market for consumption. Walnut tree is favored because of its multifunctionality, and is widely planted to meet the demand of timber supply, ecological protection and economic forest cultivation.

[0003] The processing method of green walnut has long relied on manual peeling. After picking, green walnuts are stacked and covered with something on top to maintain humidity. After waiting for the green skin to swell naturally for about 4 to 6 days, the green skin is removed one by one manually. However, this method is inefficient, consumes a lot of manpower, and poses a potential threat to the skin health of the operator during operation. The manual peeling process will face a huge workload, resulting in low efficiency and prolonged time required. More seriously, during the stacking process, the kernel is easily attacked by diseases due to the decay of the green skin, which not only greatly reduces the market value of the walnut, but also causes serious loss of nutritional ingredients.

[0004] With the vigorous development of walnut planting industry, the traditional manual shelling method cannot meet the needs of modern efficient production. In view of the existing planting and picking mode, the mechanical green skin removal method can quickly and effectively remove the green skin, which not only helps the storage of walnuts, but also provides convenience for subsequent processing.

[0005] The utility model provides a small -size walnut green skin removes cleaning machine, and the optimization innovation on the basis of traditional machine realizes the reverse rotation of built -in stirring and outer peeling screen cylinder through planetary gear transmission structure. In this way, the contact area, frequency and speed of walnut peeling can be improved, so that the efficiency and peeling effect of walnut peeling are greatly improved. UTILITY MODEL CONTENTS

[0006] In view of the above shortcomings in the prior art, the utility model provides a small -size walnut green skin removes cleaning machine, which is practical in structure and convenient to popularize.

[0007] A small -size walnut green skin removes cleaning machine, which comprises a rack, a peeling mechanism, a power mechanism and a cleaning mechanism.

[0008] The peeling mechanism is installed on the rack, and the peeling mechanism comprises an outer cylinder, an inner cylinder, a main shaft and a stirring blade.

[0009] The power mechanism comprises a motor and a V-shaped belt, the output end of the motor is connected with the V-shaped belt, and the other end of the V-shaped belt is connected with the sun gear.

[0010] The cleaning mechanism comprises a water tank, a water pump and a water inlet pipe, the water tank is fixed on one side of the rack, the water tank is provided with the water pump, one end of the water inlet pipe is connected with the water outlet of the water pump, and the other end of the water inlet pipe is connected with the top of the inner cylinder.

[0011] Preferably, the output end of the motor is connected with a speed reducer, and the output end of the speed reducer is connected with the V-shaped belt.

[0012] Preferably, the motor and the speed reducer drive the sun gear to rotate, and then drive the inner gear ring and the main shaft to rotate, and the inner cylinder and the stirring blade rotate in opposite directions.

[0013] Preferably, one side of the outer cylinder is provided with a water outlet.

[0014] Preferably, the bottom of the inner cylinder is provided with a rotating bearing, and the inner gear ring drives the inner cylinder to rotate.

[0015] Preferably, a bearing is arranged between the main shaft and the bottom of the inner cylinder, and the sun gear drives the main shaft to rotate.

[0016] Preferably, the rolling brush is a steel wire brush, and the rolling brushes are uniformly arranged and fixed in the inner cylinder.

[0017] The utility model discloses the beneficial effect is:

[0018] 1. Adopt the fully enclosed operation, has improved the stability and the security of the walnut peeling machine working process.

[0019] 2. The peeling mode that the inner cylinder and the stirring blade rotate oppositely is adopted, and the cleaning device is simultaneously increased, and the peeling effect and the peeling efficiency are improved.

[0020] 3. The device can realize rapid peeling and deep cleaning of green walnut, saves labor and improves work efficiency. BRIEF DESCRIPTION OF DRAWINGS

[0021] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings needed to be used in the embodiments will be briefly introduced as follows. It should be understood that the following drawings only show some embodiments of the present application, and therefore should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can also be obtained without creative labor on the basis of these drawings.

[0022] Figure 1 The three-dimensional structure of the present application Figure 1 ;

[0023] Figure 2 The three-dimensional structure of the present application Figure 2 ;

[0024] Figure 3 The internal structure of the present application Figure 1 ;

[0025] Figure 4 The internal structure of the present application Figure 2 ;

[0026] Figure 5 The side view of the present application

[0027] 100-stand, 200-peeling mechanism, 201-outer cylinder, 202-inner cylinder, 203-main shaft, 204-pushing blade, 205-barrel cover, 206-drainage port, 207-rolling brush, 208-inner gear ring, 209-planetary gear, 210-sun gear, 211-, 300-power mechanism, 301-motor, 302-V-belt, 303-main shaft, 400-cleaning mechanism, 401-water tank, 402-water inlet pipe. DETAILED DESCRIPTION

[0028] In order to make the purpose, technical solutions and advantages of the embodiments of the present application more clear, the technical solutions in the embodiments of the present application will be described clearly and completely in combination with the drawings in the embodiments of the present application. Obviously, the described embodiments are some embodiments of the present application, not all embodiments. The components of the embodiments of the present application described and shown in the drawings can be arranged and designed in various different configurations.

[0029] In the description of the embodiments of the utility model, it needs to be explained that, if the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer" and the like indicate the orientation or positional relationship shown in the drawings, or the orientation or positional relationship of the utility model product in common use, only for the convenience of describing the utility model and simplifying the description, and not indicating or implying that the indicated device or element must have a specific orientation, structure and operation, therefore, it cannot be understood as a limitation of the utility model. In addition, the terms "first", "second", "third" and the like are only used for distinguishing description, and cannot be understood as indicating or implying relative importance.

[0030] In addition, if the terms "horizontal", "vertical", "overhanging" and the like appear, it does not mean that the component must be absolutely horizontal or overhanging, but can be slightly inclined. For example, "horizontal" only means that its direction is relatively more horizontal than "vertical", and does not mean that the structure must be completely horizontal, but can be slightly inclined.

[0031] In the description of the embodiments of the utility model, "multiple" represents at least 2.

[0032] In the description of the embodiments of the utility model, it also needs to be explained that, unless otherwise explicitly specified and limited, if the terms "set", "install", "connect", "connect" appear, they should be understood in a broad sense, for example, can be fixedly connected, can be detachably connected, or integrally connected; can be mechanically connected, can be electrically connected; can be directly connected, can be indirectly connected through an intermediate medium, can be the communication inside two elements. For ordinary skilled in the art, the specific meaning of the above terms in the utility model can be understood according to the specific circumstances.

[0033] As shown in the drawings, a small walnut green skin removing and cleaning machine comprises a rack 100, a peeling mechanism 200, a power mechanism 300 and a cleaning mechanism 400.

[0034] The peeling mechanism 200 is mounted on the stand 100 and comprises an outer cylinder 201, an inner cylinder 202, a main shaft 203, and a paddle 204. The outer cylinder 201 is fixed to the stand 100 and has an openable lid 205 on its top. The inner cylinder 202 is located inside the outer cylinder 201 and has several drain ports 206 on its sidewall. A water outlet 211 is located on one side of the outer cylinder 201. Several wire brushes 207 are arranged on the inner surface of the inner cylinder 202 and are evenly arranged and fixed inside the inner cylinder 202. The bottom of the inner cylinder 202 is equipped with a planetary gear structure 209. This structure includes an inner ring gear 208 fixed to the bottom of the inner cylinder 202, planetary gears 209 meshing with the inner ring gear 208, and a sun gear 210 located between and meshing with the planetary gears 209. Sun gear 210 is fixed to the bottom of the main shaft 203, which is located in the center of the inner cylinder 202 and is equipped with a paddle 204. A rotating bearing is provided at the bottom of the inner cylinder 202. The rotation of the inner ring gear 208 drives the rotation of the inner cylinder 202. A bearing is provided between the main shaft 203 and the bottom of the inner cylinder 202. The rotation of the sun gear 210 drives the rotation of the main shaft 203.

[0035] The power mechanism 300 includes a motor 301 and a V-belt 302. The output end of the motor 301 is connected to the V-belt 302, and the other end of the V-belt 302 is connected to the sun gear 210. The output end of the motor 301 is connected to a reducer, and the output end of the reducer is connected to the V-belt 302. The motor 301 and the reducer drive the sun gear 210 to rotate, which in turn drives the inner ring gear 208 and the main shaft 203 to rotate, causing the inner cylinder 202 and the paddle blades 204 to rotate in the opposite direction.

[0036] The cleaning mechanism 400 includes a water tank 401, a water pump and a water inlet pipe 402. The water tank 401 is fixed to one side of the stand 100. A water pump is installed in the water tank 401. One end of the water inlet pipe 402 is connected to the water outlet of the water pump and the other end is connected to the top of the inner cylinder 202.

[0037] 1. Overall parameter calculation:

[0038] The working parameters of this walnut peeling machine are set as follows: peeling output is 600kg / h.

[0039] Next, determine the barrel parameters and operating speed of the peeling machine.

[0040] The initial setting of the cylinder working space is the large diameter D = 36cm, the small diameter d = 16cm. The cylinder height H = 47cm. It is known that green walnuts are spherical particles, the walnut particle size is generally around 30-50mm, taking the middle value of 40mm, and the walnut density ρ = 1.0-1.2g / cm 3 , take ρ = 1.1 g / cm3 Then:

[0041]

[0042] According to formula (1) and data, V1=33.5 g / cm 3

[0043] The mass of a single walnut m1.

[0044] m1=V1·p (2)

[0045] According to formula (2) and data, m1=36.8 g

[0046] The number of walnuts in a cylinder is N:

[0047]

[0048] According to formula (3) and data, N=4584 (pcs)

[0049] Because the cylinder cannot be filled with walnuts, the optimal volume ratio is 60% of the cylinder. Therefore, 4584X0.6=2750 pcs.

[0050] The integer value of N is conservatively taken as 2750 pcs. Therefore, the yield per cylinder is m=m1XN=0.037X2500=101 kg

[0051] Given that the hourly yield is 600 kg, the per-minute yield is 10 kg. Therefore, the time required per cylinder is 10 minutes. According to experimental data, the peeling speed is approximately 6 m / s for optimal peeling effect. Because the entire driving mechanism is a sun gear driving a brush roller, the diameter of the brush roller D=160 mm. Therefore, the working speed of the peeling machine driving spindle

[0052]

[0053] According to formula (4) and data, n w =716 rpm

[0054] Then the torque is calculated by formula:

[0055]

[0056] T- torque, unit N·m;

[0057] F- circumferential force, unit N;

[0058] D- diameter, unit m.

[0059] According to the design requirements, it is known that the workspace is D = 260 mm, and the weight of each barrel volume is m = 100 kg. Take the friction coefficient f = 0.25, then the circumferential force Ft = 250 N.

[0060] According to the above formula, the working torque of the peeling machine is:

[0061]

[0062] According to formula (6), the data is substituted: T = 32.5 N·m

[0063] Therefore, the final calculation parameters are sorted out, the working space of the peeling machine cylinder is D = 360 mm, the middle warp is 260 mm, the small diameter d = 160 mm, the cylinder height H = 470 mm. The required torque for work is 32.5 N·m, and the working speed is 716 r / min.

[0064] 2, motor selection design

[0065] 2.1, motor selection design

[0066] Through the above calculation, the required speed and torque of the mechanism are:

[0067] T1 = 32.5 N·mm

[0068] n1 = 716 rpm (7)

[0069] Calculate the required power of the motor:

[0070]

[0071] According to formula (7), (8), the data is substituted: P W = 2.34 kw

[0072] According to the speed and power calculation value, the three-phase asynchronous motor can meet the requirements. In order to meet the speed requirements of the work, four-stage alternating current motor can be selected combined with V-belt transmission to achieve the required speed. The following calculates the transmission efficiency:

[0073] V-belt transmission efficiency: η1 = 0.96

[0074] Bearing working efficiency: η2 = 0.99

[0075] Gear transmission efficiency: η3 = 0.97

[0076] Therefore, the total device efficiency is:

[0077]

[0078] According to formula (9), the data is substituted: η a = 0.876

[0079] Motor required input power:

[0080]

[0081] According to formula (10) and data, P d = 2.78 kw

[0082] Therefore, the selected motor model is Y00L2-4 three-phase asynchronous motor, rated power P = 3.0 kw, full load speed n m = 1430 r / min, synchronous speed n t = 1500 r / min.

[0083] Motor main external size specifications:

[0084] Table 1 Motor main parameters

[0085]

[0086] 2.2, transmission ratio distribution

[0087] According to the selected motor full load speed n w and the main shaft speed of the working machine n m , the transmission ratio of the transmission device is calculated and distributed:

[0088]

[0089] According to formula (11) and data, i a = 2.0

[0090] Therefore, the V-belt drive:

[0091] i v = 2.0

[0092] 3, main shaft design calculation and checking

[0093] 3.1 Main shaft diameter calculation

[0094] (1) The determined kinematics and dynamics parameters

[0095] Speed n = 715 r / min; motor power p d = 3.0 kw;

[0096] Main shaft power:

[0097] P = P d × η (12)

[0098] According to formula (12) and data, P = 2.76 kw.

[0099] Torque transmitted by the shaft:

[0100]

[0101] According to formula (13) and data, T = 35658 N-m

[0102] (2) Material selection of the shaft and determination of allowable bending stress

[0103] According to the relevant table, we selected 45 steel (after quenching and tempering), the hardness of the tooth surface is in the range of 217-255 HBS, and the allowable bending stress value is [σ] = 60 MPa.

[0104] (3) Roughly calculate the minimum diameter of the shaft according to the torsional strength

[0105] Since the intermediate shaft is subjected to a large bending moment and torque, A0 = 120 is taken.

[0106]

[0107] According to formula (14) and data, d = 18.6 mm.

[0108] Since there is a keyway at the minimum diameter, we take:

[0109] d min = 1.05 x d (15)

[0110] According to formula (15) and data, d min = 20 mm

[0111] Since the minimum diameter shaft section is at both sides of the input and output, plus the long working section of the roller, in order to prevent deformation, the shaft diameter is taken slightly larger. Therefore, the standard diameter d min = 45 mm is selected.

[0112] 3.2 Analysis of the structure size of the main shaft

[0113] The design of the main shaft takes into account the way of power input and output, in addition to the design of the support structure. The left side of the main shaft receives the transmitted power through the belt pulley, and the middle two sides are provided with key rotary support by the belt bearing. The right side of the main shaft is connected to the grinding wheel piece, which is responsible for the output of power.

[0114] When determining the length and diameter of each shaft section, the following steps are followed:

[0115] Section 1: The part connected with the V-belt pulley, in order to ensure stable transmission, we selected a shaft section with a diameter of d1 = 45 mm. In order to match the pulley, the length is taken as L1 = 50 mm.

[0116] 2 section: need to match with bearing, so the diameter d2 match with the bearing hole size, we choose d2 = 50mm. To match the bearing, i.e. L2 = 70mm.

[0117] 3 section: as the intermediate shaft, take diameter d3 = 60mm, length L3 = 15mm, ensure the smooth transition of the shoulder.

[0118] 4 section: diameter d4 need to match with the gear hole size, take diameter d4 = 50mm. Length L4 also to match the bearing width, i.e. L4 = 90mm.

[0119] 5 section: for the installation of the inner cylinder brush, diameter d5 = 45mm, to match the brush width, take L5 = 480mm. By such design, the spindle can meet the power transmission and support requirements, and the length and diameter of each shaft section can also be determined reasonably.

[0120] Table 2 length parameters of each shaft section

[0121] Shaft segment 1 2 3 4 5 Diameter (mm) 45 50 60 50 45 Length (mm) 50 70 15 90 480

[0122] 3.3 combined strength check of bending and torsion

[0123] 1. When calculating the force on the shaft, the effect of each force on the shaft should be considered. Among them, FT1 is the circumferential force of pulley 1, the size of this force depends on the diameter d1 of pulley 1, then

[0124]

[0125] According to formula (16), the data is substituted to get: F t2 = 356N

[0126] The circumferential force of gear 2 (d2 is the diameter of the gear)

[0127]

[0128] According to formula (17), the data is substituted to get: F t2 = 368N

[0129] 2. Calculate the reaction force acting on the shaft

[0130] The distance from pulley to the midpoint of bearing L a = 68mm, the distance from bearing to the midpoint of gear L b = 65mm, the distance from the gear shaft to the drum shaft L c = 305mm.

[0131] According to the force, the formula is:

[0132]

[0133] According to equation (18), R = 60N A

[0134] Counterforce of bearing 2:

[0135] R B = F t1 +F t2 -R A (19)

[0136] According to equation (19), R = 330N. B

[0137] By drawing the bending moment diagram, we can know that:

[0138] Bending moment at support A:

[0139] M A = F t1 ×L a (20)

[0140] According to equation (19), M = 2740N·mm. A

[0141] Bending moment at support B:

[0142] M B = R A ×(L b / 2)-F t1 ×(L b / 2+L a ) (21)

[0143] According to equation (17), M = 1855N·mm. B

[0144] Bending moment at support C:

[0145] M C = R A ×(L b +L c )+R B ×L c -F t1 ×(L a +L b +L c ) (22)

[0146] According to equation (17), M = 22507N·mm C

[0147] 3. By drawing the torque diagram, we can know that: T = 35658N·mm ​​​​​

[0148] 4. By drawing the equivalent bending moment diagram, we have:

[0149]

[0150] According to formula (23), we have: M VA = 28319 N-mm

[0151] M VB = 31054 N-mm

[0152] M VC = 18255 N-mm

[0153] Since the bending moment at shaft b is large, the section is also subjected to torque, i.e.

[0154] Bending section modulus:

[0155]

[0156] According to formula (24), we have: W = 9112.5 mm 2

[0157] Torsion section coefficient is:

[0158]

[0159] According to formula (25), we have: W r = 18225 mm 3

[0160] Maximum bending stress is:

[0161]

[0162] According to formula (26), we have: σ = 3.4 Mpa

[0163] Shear stress is:

[0164]

[0165] According to formula (27), we have: t = 1.7 Mpa

[0166] When checking calculation, the strength of bending and torsion is considered. For single-direction transmission shaft, the torque characteristics are considered, so the corresponding conversion coefficient α = 0.6 is selected, and the equivalent stress is:

[0167]

[0168] According to formula (23), we have: σ ca = 4.0 Mpa

[0169] From the table, the ultimate tensile strength σ B = 640 MPa, the allowable bending stress of the shaft [σ-1b] = 60 MPa, σ < e < [σ-1b], so the strength meets the requirements.

[0170] 3.4, the selection and checking of the key

[0171] 1. The key connection of shaft I and pulley

[0172] 1) From the design of the shaft, the key C10x8x72 is initially selected, T I = 37.84 N.m

[0173] 2) Check the strength of the key connection

[0174] The materials of the key, shaft and hub are all steel, and according to the textbook, the allowable stress [σ] = 100-120 MPa, take σ = 110 MPa. The working length of the key l = L-b / 2 = 72 mm-5 mm = 68 mm, the contact height of the key and the hub keyway k = 0.5h = 0.5x8 = 4 mm

[0175]

[0176] According to formula (29), substituting the data: σ p = 8.69 MPa

[0177] It can be seen that the strength of the connection is sufficient, and the key C10x8x72 is determined to be selected.

[0178] 2. The key connection of gear 1 and shaft II

[0179] 1) From the design of shaft II, the key 10x8x28 is initially selected, T = T II / 2 = 65.42 N.m

[0180] 2) Check the strength of the key connection

[0181] The materials of the key, shaft and hub are all steel, and according to the textbook, the allowable stress Take [σ P ] = 110 MPa. The working length of the key l = L-b = 28 mm-10 mm = 18 mm, the contact height of the key and the hub keyway k = 0.5h = 0.5x8 = 4 mm.

[0182]

[0183] According to formula (30), substituting the data: σ P = 51.92 Mpa

[0184] It can be seen that the strength of the connection is sufficient, and the key 10x8x28 is determined to be selected.

[0185] Gear 2 and the key connection of shaft III

[0186] 1) The design of shaft III initially selects the key 10 x 8 x 28, T = T III / 2 = 345.92 N·m

[0187] 2) Check the strength of the key connection

[0188] The materials of the key, shaft and hub are all selected to be steel. According to the textbook, the allowable stress [σ P ] = 100-120 MPa, take [σ P ] = 110 MPa. The working length of the key l = L-b = 28-10 = 18 mm, and the contact height of the key and the hub keyway k = 0.5h x 11 mm = 5.5 mm.

[0189]

[0190] According to formula (23), substituting the data gives: σ P = 41.93 MPa

[0191] It can be seen that the strength of the connection is sufficient, and it is determined to select the key 10 x 8 x 28.

[0192] 4, V-belt drive design

[0193] 4.1 Known conditions and design content

[0194] When designing the V-belt, the known conditions need to be first clarified: the required rated power p d = 3.0 kw, the speed of the small pulley n1 = 1430 r / min n1, the transmission ratio i = 2.0. The design content includes determining the V-belt model, length and required number, in addition to calculating the diameter, width of the pulley and the center distance of the shaft hole diameter, further calculating and determining the initial tension force, and the specific direction and size of the force acting on the shaft.

[0195] 4.2 Design calculation steps (1) Determine the calculation power Pca

[0196] The working condition coefficient K A = 1.2 is obtained from the table, so:

[0197] P ca = K A × P (32)

[0198] According to formula (32), substituting the data gives: P ca = 3.34 kw

[0199] (2) Select the V-belt belt type

[0200] According to P ca, n1 can be selected as A type.

[0201] 1) The reference diameter of the small pulley is selected as d d1 = 100 mm. d1

[0202] 2) The belt speed v is checked:

[0203]

[0204] According to formula (33), the data is substituted to get v = 7.5 m / s

[0205] Since 5 m / s < v < 30 m / s, the requirement is met, and ε = 0.02 is taken.

[0206] (3) The reference diameter of the large pulley is calculated. The reference diameter of the large pulley d

[0207] d d2 = i x d d1 x (1-ε) (35)

[0208] According to formula (36), the data is substituted to get d d2 = 196 mm

[0209] According to the table, the standard value is taken as d d2 = 200 mm.

[0210] (4) The center distance a of the V-belt and the reference length L d are determined. According to the table, the center distance a0 = 240 mm is taken.

[0211] The reference length of the V-belt:

[0212]

[0213] According to formula (36), the data is substituted to get L d0 = 961 mm

[0214] According to the table, the reference length of the belt L d = 1000 mm, and the actual center distance a is calculated according to the formula.

[0215]

[0216] According to formula (37), the data is substituted to get a = 259 mm

[0217] (5) The wrap angle α of the small pulley is checked:

[0218]

[0219] According to formula (38), the data is substituted to get α1 ≈ 157.8°​

[0220] (6) Calculate the number of belts z

[0221] 1) Calculate the rated power of a single V-belt Pr.

[0222] From dd1 = 100 mm and n1 = 1430 r / min, look up table to get P0 = 1.32 kW.

[0223] According to n1 = 1430 r / min, i = 2.0 and A type belt, look up table to get Δp0 = 0.17 kw.

[0224] Look up table K α = 0.95, K L = 0.99, so:

[0225] P r = (P0 + ΔP0) x K a x K L (39)

[0226] According to formula (39) and data: P r = 1.4 kw

[0227] 2) Calculate the number of belts z

[0228]

[0229] According to formula (40) and data: Z = 2.38, so take 3.

[0230] (7) Calculate the initial tension of a single V-belt F0

[0231] From the table, the unit length mass of the A type belt q = 0.105 kg / m, so

[0232]

[0233] According to formula (23) and data: F0 = 127 N

[0234] (8) Calculate the pressing shaft force Fp

[0235]

[0236] According to formula (42) and data: F p = 748 N

[0237] Table 3 Main parameters of belt and pulley

[0238] Belt type A Center distance 259 mm Small pulley reference diameter 100 mm Wrap angle 157.9° Large pulley reference diameter 200 mm Belt length 1000 mm Number of belts 3 Initial tension 127N Belt speed 7.5 m / s Pressing force 748N

[0239] 4.3, Pulley structure design

[0240] (1) The structural design of the small pulley

[0241] The shaft hole diameter d of the small pulley is 28 mm, and d d1 = 100 mm < 300 mm, so the small pulley is selected as a web type.

[0242] The size of the small pulley is as follows:

[0243] d1 = 2.0 x d (43)

[0244] According to the formula (43), the data is substituted to obtain d1 = 56 mm

[0245] d a = d d1 + 2 x h a (44)

[0246] According to the formula (44), the data is substituted to obtain d a = 105.5 mm

[0247] B = (z - 1) x e + x f (45)

[0248] According to the formula (45), the data is substituted to obtain B = 48 mm

[0249] C = 0.25 x B (46)

[0250] According to the formula (46), the data is substituted to obtain C = 12 mm

[0251] L = 2.0 x d (47)

[0252] According to the formula (47), the data is substituted to obtain L = 56 mm

[0253] (2) The structural design of the large pulley

[0254] The shaft hole d of the large pulley is 45 mm, and d d2 = 200 mm, so the large pulley is selected as a spoke type.

[0255] The size of the large pulley is as follows:

[0256] d1 = 2.0 x d (48)

[0257] According to the formula (48), the data is substituted to obtain d1 = 90 mm

[0258] d a2 = d d2 + 2 x h a (49)

[0259] According to the formula (49), the data is substituted to obtain d a2 = 205.5 mm

[0260] B = (z - 1) x e + 2 x f (50)

[0261] According to formula (50) and data, B = 48 mm

[0262]

[0263] According to formula (51) and data, hi = 33.6 mm, h2= 26.9 mm, bi = 13.4 mm, b2= 10.75 mm, fi = 6.72 mm, f2= 5.4 mm

[0264] L = 2.0 x d (52)

[0265] According to formula (52) and data, L = 90 mm

[0266] 5. Gear transmission design

[0267] 5.1. Initial condition selection

[0268] According to the gear structure characteristics, the main modification gear is to adjust the transmission direction and output form of power, and it does not undertake the task of speed reduction itself, so its speed reduction ratio is set to 1, indicating that the speed remains unchanged during power transmission.

[0269] (1) The material of a set of meshing gears is selected as 45 (quenching and tempering), and the tooth surface hardness is 240 HBS

[0270] (2) The outer diameter of the cylinder working space is D = 340, and the inner diameter is d = 180. Therefore, the gear ratio i = 1.8, and the pinion gear tooth number Z1= 25

[0271] (3) The pressure angle a = 20°

[0272] 5.2. Design according to tooth surface contact fatigue strength

[0273] (1) Calculate the gear pitch circle diameter, that is,

[0274]

[0275] 1) Determine the parameter values

[0276] ① Load coefficient K Ht = 1.3

[0277] ② Gear transmission torque:

[0278] According to formula (53) and data, T = 35658 N·mm

[0279] According to the table, we have:

[0280] ③ φd= 0.125

[0281] (4) Zone coefficient Z H = 2.46

[0282] (5) Elastic influence coefficient Z E = 189.8 MPa

[0283] (6) In order to determine the durability of the material under the condition of contact fatigue, then:

[0284] σ Hlim1 = 600 Mpa

[0285] σ Hlim2 = 500 Mpa

[0286] The contact fatigue coefficient is obtained from the figure:

[0287] K HN1 = 0.972

[0288] K HN2 = 0.994

[0289] Taking the failure probability as 100 and the safety factor S = 1, we get

[0290]

[0291] According to formula (54), the data is substituted to get: [σ H ]1= 583 Mpa

[0292]

[0293] According to formula (55), the data is substituted to get: [σ H ]2= 574 Mpa

[0294] The contact fatigue allowable stress of the gear pair is taken as the smaller value of [σ H ]1, [σ H ]2, that is, [σ H ]= 574 MPa

[0295] 2) Trial calculation of pinion pitch circle diameter

[0296]

[0297] According to formula (56), the data is substituted to get: d 1t = 49 mm

[0298] (2) Adjust the pitch circle diameter of the pinion

[0299] 1) Data preparation before calculating the actual load coefficient.

[0300] Tooth width b:

[0301]

[0302] According to formula (57) and data, b = 32 mm

[0303] 2) Actual load coefficient K H

[0304] 1.25 A

[0305] 2) Dynamic load coefficient K V = 1.09

[0306] 3) Circumferential force of gear

[0307]

[0308] According to formula (58) and data, F t = 1454 N

[0309]

[0310] According to formula (59) and data, K A = 29.5 mm < 100 N

[0311] According to relevant table, determine the load distribution coefficient K Hα = 1.2, the load distribution coefficient K Hβ = 1.2, then

[0312] K H = K A × K V × K Hα × K Hβ (60)

[0313] According to formula (60) and data, K H = 1.96

[0314] 3) The pitch circle diameter calculated according to the actual load coefficient

[0315]

[0316] According to formula (61) and data, d d1 = 59 mm

[0317] 4) Determine the modulus

[0318]

[0319] According to formula (62) and data, m n = 2.39 mm, so m n = 3.0 mm. ​

[0320] 5.3 Planetary gear calculation

[0321] The smallest gear by calculation According to the above calculation, Z B = 1.8 x Z A So Z B = 1.8 x Z A = 1.8 x 62 = 112.

[0322] These conditions meet Z A / n w ≠ integer Z B / n w ≠ integer, and Z B / Z C and Z A / Z C No common divisor, C / n ≠ integer NGW type gear requirement, and Z B > 100 is not a prime number, in order to facilitate processing.

[0323] 5.4 Check the bending fatigue strength of the tooth root

[0324] The tooth root bending fatigue strength condition is:

[0325]

[0326] 1) K, T, m n , d1 same as before

[0327] Tooth width b1 = b2 = 25

[0328] Tooth profile coefficient Y Fa , stress correction coefficient Y Sa The calculation needs to determine the equivalent number of teeth first:

[0329]

[0330] According to formula (63) and data: Z V1 = 25

[0331] The equivalent number of teeth of the large gear:

[0332]

[0333] According to formula (64) and data: Z V2 = 112

[0334] Look up table:

[0335] Y Fa1 = 2.52, Y Fa2 = 2.136

[0336] Y Sa1 = 1.62, Y Sa2 = 1.837

[0337] The tooth root bending fatigue limit of the pinion and the gear are found to be:

[0338]

[0339] The bending fatigue coefficient is found from the figure:

[0340] K FN1 = 0.774, K FN2 = 0.083

[0341] Taking the bending fatigue safety factor S = 1.4, the allowable bending stress

[0342]

[0343] According to formula (65) and substituting the data, we get: [σ F ]1 = 276.429 Mpa

[0344]

[0345] According to formula (66) and substituting the data, we get: [σ F ]2 = 239.67 Mpa

[0346]

[0347] According to formula (67) and substituting the data, we get: σ F1 = 72.399 Mpa < [σ F ]1

[0348]

[0349] According to formula (68) and substituting the data, we get: σ F2 = 69.59 Mpa < [σ F ]2

[0350] Therefore, the bending strength is sufficient.

[0351] 5.5 Geometric size calculation

[0352] To carry out the geometric calculation of high displacement gear transmission, the geometric parameters of the three wheels A, B and C must be determined first

[0353] 1) The pitch circle diameter

[0354] According to formula (69) and substituting the data, we get:

[0355] 2) Addendum height

[0356]

[0357] According to the formula (70) and substituting the data, h aAII = 3.0 mm

[0358] h aCII = 3.0 mm

[0359] h aBII = 3.0 mm

[0360] 3) Addendum

[0361]

[0362] According to the formula (71) and substituting the data, h fAII = 3.75 mm

[0363] 4) Dedendum

[0364] According to the formula (72) and substituting the data,

[0365] d aBII = 342 mm

[0366] 5) Root diameter

[0367] d fAII = d AII - 2h fAI (73)

[0368] According to the formula (73) and substituting the data, d fAII = 178.5 mm

[0369] d fCII = 67.5 mm

[0370] d fBII = 328.5 mm

[0371] 6) Tooth width

[0372] Referring to the table 13-1-79 of the Machinery Design Handbook, that is, the recommended range table of tooth width coefficient ψ d

[0373] Referring to the table, ψ d = 0.25 ~ 0.8, and ψ d = 0.25 is taken

[0374] Sun gear tooth width b A: b A = ψ d d AII ​= 0.25 x 186 = 46.5 mm take b A = 50 mm

[0375] Row wheel tooth width b C : take b C = 50 mm;

[0376] Internal gear tooth width b B : b B = 50 mm.

[0377] 2, stress analysis of main parts

[0378] Through the analysis and calculation, the maximum stress of the main shaft is 1.478x10 N / m2, which is less than the yield force 1.850x102 N / m2, the maximum displacement variable of the main shaft relative to the rotation center is 9.574x10-2 mm, the displacement variable is small, the maximum strain value is 5.462x10-4 mm, and the strain is also small, therefore, the design structure strength of the main shaft of the small walnut green skin removing and cleaning machine meets the working requirements.

[0379] The design mainly aims at the green walnut peeling and cleaning machine, and is in-depth researched and designed. The feeding device and the peeling device are improved and the layout is optimized during the design process. In addition, the modular design is adopted in the structure design. The structure design of the green walnut peeling machine is optimized, the fully-closed operation is adopted, and the stability and safety during the working process are improved. The peeling mode of opposite rotation of the inner and outer cylinders is adopted, and the cleaning device is additionally arranged, so that the peeling effect and the peeling efficiency are improved. The utility model can realize the rapid peeling and deep cleaning of the green walnut, the peeling speed can reach 1000 kg / h, the breakage rate of the walnut is less than 3%, the peeling rate is high and reaches more than 95%, and the requirements are met.

[0380] The above only describes the preferred embodiment of the utility model patent, and does not limit the utility model patent, and any modification, equivalent replacement and improvement within the spirit and principle of the utility model patent should be included in the protection range of the utility model patent.

Claims

1. A small walnut green husk removing and cleaning machine, characterized in that, The device comprises a rack (100), a peeling mechanism (200), a power mechanism (300) and a cleaning mechanism (400). The peeling mechanism (200) is installed on the rack (100), and comprises an outer cylinder (201), an inner cylinder (202), a main shaft (203) and a stirring blade (204). The outer cylinder (201) is fixed on the rack (100), and a bucket cover (205) is arranged on the top of the outer cylinder (201). The inner cylinder (202) is located inside the outer cylinder (201), and a plurality of drainage openings (206) are arranged on the side wall of the inner cylinder (202). A plurality of rolling brushes (207) are arranged on the inner surface of the inner cylinder (202). A planetary gear (209) structure is arranged at the bottom of the inner cylinder (202), and comprises an inner ring gear (208) fixed at the bottom of the inner cylinder (202), a planetary gear (209) in meshing connection with the inner ring gear (208), and a sun gear (210) located in the middle of the planetary gear (209) and in meshing connection with the planetary gear (209). The sun gear (210) is fixed at the bottom of the main shaft (203), and the main shaft (203) is located in the middle of the inner cylinder (202). The stirring blade (204) is installed on the main shaft (203). The power mechanism (300) comprises a motor (301) and a V-shaped belt (302). The output end of the motor (301) is connected with the V-shaped belt (302), and the other end of the V-shaped belt (302) is connected with the sun gear (210). The cleaning mechanism (400) comprises a water tank (401), a water pump and a water inlet pipe (402). The water tank (401) is fixed on one side of the rack (100), and the water pump is arranged in the water tank (401). One end of the water inlet pipe (402) is connected with the water outlet of the water pump, and the other end of the water inlet pipe (402) is connected with the top of the inner cylinder (202).

2. The small walnut green husk removing and cleaning machine according to claim 1, characterized in that: The output end of the motor (301) is connected with a speed reducer, and the output end of the speed reducer is connected with the V-shaped belt (302).

3. The small walnut green husk removing and cleaning machine according to claim 2, characterized in that: The motor (301) and the speed reducer drive the sun gear (210) to rotate, and then drive the inner ring gear (208) and the main shaft (203) to rotate. The inner cylinder (202) and the stirring blade (204) rotate in opposite directions.

4. The small walnut green husk removing and cleaning machine according to claim 1, characterized in that: A water outlet (211) is arranged on one side of the outer cylinder (201).

5. The small walnut green husk removing and cleaning machine according to claim 1, characterized in that: A rotating bearing is arranged at the bottom of the inner cylinder (202), and the inner ring gear (208) drives the inner cylinder (202) to rotate.

6. The small walnut green husk removing and cleaning machine according to claim 1, characterized in that: A bearing is arranged between the main shaft (203) and the bottom of the inner cylinder (202), and the sun gear (210) drives the main shaft (203) to rotate.

7. The small walnut green husk removing and cleaning machine according to claim 1, characterized in that: The rolling brushes (207) are steel wire brushes, and are uniformly arranged in the inner cylinder (202).

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