A telescopic platform is equipment used in the Laboratory or Workshop to carry out different kinds of job on the ceiling e.g. fixing or replacing of electric bulbs, fixing of electric fans etc. it is also used to change streetlight on campus. Now that technology changes rapidly, the use of step ladders of different kinds with low reliability and quite a number of limitations should gradually be replaced by less expensive alternative. To this end, Telescopic Platform has been designed and constructed to meet the urgent need for replacement. Materials were locally sourced for such as Bevel gear, Sprockets, Chain, Power scr ew, Nut etc. and used for the fabrication, which involves welding grinding, fitting practices as well as assembly. The Telescopic Platform so produced is mobile, suitable for use on flat, sloping and terraced surfaces with high reliability. Its height can be varied within a range designed. The telescopic platform designed can offer a good capacity of 834 N with efficiency of 85% and can conveniently carry an average human weight of 736 N.
The convectional platform or stepladder for internal use within building has a few imitations. It can only be used on plane surfaces. It becomes unstable on a slope or a terraced floor. Moreover, the stepladder is of fixed height. If such a platform is to be built for changing the light bulbs in a workshop which is 6.5 metres high, it will be too big for easy movement and storage. As a result of these limitations, the telescopic platform is designed such that it can be used on a plane, a sloping as well as a terraced floor. Unlike the stepladder, the platform level is adjustable. The platform can therefore be set for use at various heights. At its lowest height it is handy for ease of storage and movement.
Other devices in the same category with telescopic platform include jack which is portable hand operated device for raising heavy weight through short distances, exerting great pressure, or holding assembled work firmly in position, as in jacking up a building to prevent settling or keep in position while replacing a foundation [
Another example is a crane, which is a device that not only lifts heavy objects but also shifts them horizontally. Cranes are distinct from hoists, passenger elevators and other devices intended solely or primarily for vertical lifting and from conveyors, which continuously lift or carry bulk materials such as grain and coal. Cranes have come into their present widespread application only since the introduction of steam engines, internal combustion engines, and electric motors beginning in the nineteenth century [
Conveyor is any or various device that provides mechanized movement of materials, as in a factory; they are used primarily in industrial applications but also in large farms, in warehousing and freight handling, and in movement of raw materials. Conveyor may be only a few inches in length, or they may be integrated systems several miles long [
Most modern elevators are propelled by electric motors with the aid of a counterweigh, through a system of cables and pulleys by opening a decisive role in a characteristic urban geography of many modern cities especially in United State, and promises to fill aim indispensable role in future city developments. The practice of lifting load by mechanical means during building operations goes to at least Roman architect-engineer Vitrullius in the 1st century BC described lifting platforms that use pulleys and capstans, or windlasses, operated by human, animal, or water power. Steam power was applied in such devices in England by 1800 [
With the safety, speed and height problems overcome, attention was turned to convenience and economy. In 1915, so called automatic leveling was introduced in the form of automatic controls at each floor that took over when the operator short off his manual control within a certain distance from the floor level and guided the car to a precisely positioned stop. Power control of door was added. With increase building height, elevator speed increased to 365 metres per minute is such installations as those for the upper levels of the Empire State Building (1931) and reached 549 metres per minute in the John Hancock center, Chicago in 1970 [
The following components were required for the production of telescopic platform:
1) The screw pair
2) Bevel gear
3) Chain drives
The materials required for the production of the components of this telescopic platform are as shown in
| S/n | Component | Possible | Selected | Reason for selection |
|---|---|---|---|---|
| Screw Gear Top baring stand power screw nut | Mild steel Mild steel Mild steel Mild steel | Can be rolled or drawn, high ductility and good heat treatment and cold working, readily weldable, low strength, high ductility, hardenable by surface hardening process, readily formed into intricate shape because of its low carbon, good heat treatment and cold 110 - 150 brinel 110 - 150 elongation of 25% - 40% can be rolled. | ||
| 2 | Sol plate Floorplate Shin cover | Galvanized Metal sheet | Excellent corrosion, water and oil from shaft deflection frame distortion, properties. | |
| 3 | Bearing | High carbon chromium steel (self-aligning: and internally sealed) | Compensate for misalignment arising from shaft deflection frame distortion, or foundation deflection. | |
| 4 | Sprocket | Iron | High compressive strength, good damping characteristics, high torsional strength, low notch sensitivity, low tensile strength, good casting properties, good anti-friction properties, good machineability and rigidity. |
Capacity of platform = 1000 N.
Maximum load on screw = 1500 N. Moment of inertia
I = π d c 4 64 (1)
The crippling load required
P = π 2 E I 4 L 2 = π 3 E d c 4 256 L 2 (2)
The core diameter of screw is 28 mm.
Therefore designing for screw of 28 mm core diameter, selection was made from the table of basic dimensions for square threads in mm. (normal stress according to IS 4694-1968): Major diameter, (d0) =34 mm; pitch (p) = 6 mm and mean diameter, dm= 31 mm of screw were selected.
P = 6 mm; do = 34.5 mm; D = 55 mm; H = 3.0 mm; L = 3p; (18 mm) θ = 5.70 μ = 0.1 = tanθ; α =10.47˚ Efficiency of screw (η)
η = tan α tan ( α + θ ) (3)
η = 63.7 %
Design analysis for the force (P) and Torque (T) of the screws with mean diameter (dm) 31 mm. Horizontal force at the screw thread.
P = w tan ( α + θ ) (4)
P = 870 N
Torque at the Screw
T = P r = ( P × d m 2 ) (5)
T = 13485 N ⋅ mm
Compressive stress on the screw cross-section
σ c = W / A (6)
σ c = 4.872 N / mm 2
where W is the designed load on the screw and A is the area of the screw shaft.
τ = T r J (7)
τ = 3.129 N / mm 2
Maximum Shear due to combined torsion and direct stresses ( τ m )
τ m = { 1 2 ( σ c 2 + 4 τ 2 ) } 1 / 2 (8)
τ m = 3.965 N / mm 2
To check the screw thread for bearing, shear and bending stresses, bearing pressure on screw thread must be equal to that on the nut thread. Allowing a bearing pressure of 0.8 N/mm2 on the nut thread, shear stress on screw thread, ( τ s )
τ s = W 2 π r c n h (9)
τ s = 0.874 N / mm 2
σ b = 3 W L 2 π r n h 2 = 2.37 N / mm 2 (10)
The arrangement in the gearbox is as shown in
Specification:
Velocity ratio V.R (5:3)
Pinion diameter,
DP(60 mm)
Ear diameter, Dg (100 mm)
Face width, b (25 mm)
Material (Steel)
Gear torque Tg= Torque at Screw/Efficiency of Screw
T g = 21170 N ⋅ mm (11)
Pinion torque T P = T g × D P D g (12)
T P = 12700 N ⋅ mm
For the velocity ratio (V.R)
V . R = Pinion revolution per minute Manual turning per minute (13)
V . R = 104.17 50 = 2.1
Chain and sprockets selection (Holowenko, 1983)
For driven Sprocket:
Nt2 = 18; P = 14 mm
The Pitch dameter, D 2 = 2 N t 2 P 2 π (14)
D 2 = 80.2 mm
For driver wheel:
Nt1 = 40; Pitch, P =14 mm
The Pitch dameter, D 1 = 2 N t 1 P 2 π (15)
D 1 = 178.25 mm
The Velocity ratio, V.R
V . R = OutputSpeed , n 2 InputSpeed , n 1 = N t 1 N t 2 (16)
V . R = 2.22
For the roller chain
Pitch, P = 14 mm; d = 5 mm; N = 5 mm
Therefore chain length L
L = 2 C + π ( R 1 + R 2 ) + ( R 1 + R 2 ) 2 C (17)
L = 2808 mm
Torque required at pinion (Tp) taking efficiency to be 90%
Torque at the driven sprocket,
T P = T d n ⋅ D 1 D 2 (18)
T P = 31360 N / mm
Torque required of handle with length 180 mm (L)
τ h = τ d r L (19)
τ h = 175 N
The shaft is fully supported by the base of the platform so that it is not under much stress. The shaft was manufactured from solid drawn steel tubing to the following specification;
Inside diameter, D1= 55.0 mm; Outside diameter, D2= 65 mm; Length, L = 2400 mm.
The support legs of the platform were made from steel rods. Step ladder was attached to one of the legs to enable the operator climb unto the platform.
The support legs are attached to the shaft through flange ball bearings to allow for the rotation of the legs around the shaft. Weight of platform plus load on platform (W) (4000 N).
The direct load on the Cross-section of the support legs. Since there are four legs, therefore;
4 cos θ = W T F
F = W T 4 cos θ (20)
F = 1000 ( 4 cos 29.36 ∘ ) = 1147.4 N
Direct stress on the Cross-Section of the support legs
σ = F π d 2 / 4 = 3.65 N / mm 2 (21)
The jacks were manufactured to the following specifications; minor diameter dm(14.60 mm); normal diameter dn(19.10mm); length,L(300 mm) and material selected was made from 0.25 C steel.
The pressure plate was made from Cast iron and the screw attached to it through a ball and socket joint to allow for self-alignment.
Compressive stress of the screw cross-section.
Total weight of platform plus load WT = 4000 N compressive stress on screw.
Cross-Section
σ c = W T π d c 2 / 4 = 4 × 4000 π × ( 14.6 ) 2 = 23.893 N / mm 2 (22)
This stress is sufficiently low compared to the Ultimate compressive stress of 430 N/mm2.
The materials used in the construction were obtained from various sources. The power screw, gearbox, nut, bevel gear, shaft and other parts of the materials were bought from the market.
The major work done in the construction were cutting, filing and welding. There was very little machining. The construction process is as follows:
The nut was screwed into the power screw, which had already been attached to the gear box. The stopper was then machined to slide into the power screw and to just slide into the shaft. It was then welded to the end of the screw.
1) Sliding the stopper and screw down the shaft the nut was brought into position at the upperpart of the shaft welded.
2) The platform was fixed on top of the gearbox and the gear made from steel rod fixed to the top of the platform.
3) The Chain drive was then assembled as specified in the design.
These costs include material cost, direct labour cost and overhead cost. All of these costs were incurred during the equipment fabrication stage.
The cost of raw materials purchased for the fabrication of the machine (Tables 2-4).
| S/n | Component | Material | Specification | Quantity | Unit price (N) | Amount (N) |
|---|---|---|---|---|---|---|
| 1 | Floor plate | Mild steel | 700 × 500 mm | 1 | 1500 | 1500 |
| 2 | Chain cover | Mild steel | 900 mm | 1 | 1200 | 1200 |
| 3 | Chain | 800 mm | 1 | 500 | 500 | |
| 4 | Bearing “small” | Cast iron | Ѳ 60 | 4 | 600 | 2400 |
| 5 | Bearing “big” | Cast iron | Ѳ 150 | 1 | 1500 | 1500 |
| 6 | Top bearing | Steel | 1000 mm | 1 | 500 | 500 |
| 7 | Power screw | Mild steel | 1750 mm | 1 | 1500 | 1500 |
| 8 | Big nut | Bronze | 460 | 1 | 500 | 500 |
| 9 | Gear box | Mild steel | 1 | 1000 | 1000 | |
| 10 | Bevel gear | Mild steel | Ѳ 350 × Ѳ 200 | 2 | 1000 | 1000 |
| 11 | Sole plate | Mild steel | 1 | 300 | 300 | |
| 12 | Shaft | Mild steel | 2300 mm | 1 | 7000 | 7000 |
| 13 | Supporting leg | Steel | 2500 mm | 4 | 500 | 2000 |
| 14 | Brazing | Steel | 100 mm | 4 | 250 | 1000 |
| 15 | Ladder | Steel | 1500 × 200 mm | 1 | 2000 | 2000 |
| 16 | Big sprocket | Cast iron | Ѳ 400 | 1 | 1200 | 1200 |
| 17 | Small sprocket | Cast iron | Ѳ 100 | 1 | 700 | 700 |
| 18 | Guide rail | Steel | 6 | 400 | 2400 | |
| Total | 32,000 | |||||
| S/n | Component | Description | Quantity | Unit price (N) | Amount (N) |
|---|---|---|---|---|---|
| 1 | Guide rail | 700 × 500 mm | 1 | 1000 | 1000 |
| 2 | Chain cover | 900 mm | 1 | 750 | 750 |
| 3 | Ladder | 800 mm | 1 | 1000 | 1000 |
| 4 | Supporting leg | 2500 mm | 4 | 750 | 3600 |
| 5 | Assembly miscellaneous | 3000 | 3000 | ||
| Total | 8750 | ||||
| S/N | Description | Quantity |
|---|---|---|
| 1 | Turning handle | 1 |
| 2 | Big and small | 1 each |
| 3 | Rail guide | 6 |
| 4 | Rail guide | 8 |
| 5 | Floorplate | 1 |
| 6 | Chain cover; chain | 1 each |
| 7 | Bearing “small” | 4 |
| 8 | Bearing “big” | 1 |
| 9 | Top bearing stand | 1 |
| 10 | Power bolt | 1 |
| 11 | Big nut | 1 |
| 12a,b | A pair of bevel gear | 1 |
| 13 | Platform | 1 |
| 14 | Sole plate | 1 |
| 15 | Upright stand | 1 |
| 16 | Supporting leg | 4 |
| 17 | brazing | 4 |
| 18 | ladder | 1 |
Cost Summary
Material Cost = N32,200
Fabrication Cost = N8750
Overhead Cost = N10,000
Grand Total = N50,950
The telescopic platform designed offers a good capacity of 834 N which can conveniently support an average human weight of 736 N. The height of the equipment is 6.2 m and thus it can be used to change the streetlights on campus and also in the workshops. As concerned farm harvesting of fruits and trimming of palm front leaves, this can serve these purposes. The production cost of this telescope platform is N50,950 which is $141.53 US Dollar using the current exchange rate of N360 per Dollar.
The efficiency of the machine can be calculated below:
Efficency = Average capacity of machine × adjustment factor Average human weight × 100 = 85 %
The telescopic platform has an average efficiency of 85% which can give a reasonable performance in use.
The proposed Telescopic Platform has been successfully designed, fabricated and tested and found capable of lift and sustain a weight of 736 N. But getting to a load of 800 N, there was buckling developed by the supporting shaft as well as shear at some welding joints. The maximum load recommended on this platform is 750 N for safety assurance.
The design and construction of a telescopic platform had been carried out, and can meet the urgent need for the replacement of electric bulbs, and fixing of fans in the workshop. It can also be used for the erection of streetlights on campus; more so, it can meet the requirement of painting in high building as well as some activities as concerned harvesting of fruits, pruning of branches and removal of epiphytes.
Although this design satisfies the requirement of the purpose for which the platform is meant, considerable improvement can still be made in the following areas:
1) Operation: to save the operator the task of raising the platform manually, the platform can be redesigned such that the screw will be driven through the gars by an electric motor. This of course will increase the production cost.
2) Minimum platform level: it can be observed that the screw-pair principle employed in the design only serves to reduce the minimum platform level to about half the maximum level. This level is too high for compactness and storage when the platform is fully telescoped.
The minimum platform level can be reduced considerably by redesigning the platform using the strut and cylinder principles, in which the platform be raised or lowered by feeding hydraulic working fluid into hydraulic telescopic rams which will for the stalk of the platform. The working fluid can be fed to the rams by pumps which can be operated either manually or electrically.
Using this principle, the minimum platform level can be reduced to one―third of the maximum level.
Authors hereby acknowledge the Head of Department of Industrial and Production Engineering of Federal University of Technology Akure, Nigeria; for release of found and the workshop tools required for the production of this product. Also we can not but appreciate Engr. J. O. Fasan the Technician that carried out the fabrication of this platform.
The authors declare no conflicts of interest regarding the publication of this paper.
Olufemi, A.B., Sola, O.T. and Jimoh, Y.A. (2018) Design and Construction of a Telescopic Platform. Open Access Library Journal, 5: e4784. https://doi.org/10.4236/oalib.1104784
σc = compressive stress (N/mm2)
ϵ = young’s modulus (N/mm2)
Ls = lead of the screws
P = pitch of the thread
I = moment of inertia
L = unsupported length
n = factor of safety
W = design load (N)
dc = core diameter
Do = outside diameter(mm)
do = major diameter of nut (mm)
H = depth of thread (mm)
η = Efficiency (%)
θ = Friction angle (˚C)
α = Helix angle
π = constant
dm = Mean diameter
Ʈ = Torsion stress
Ʈs = Share stress
σb = bending stress
A = Area of the screw shaft (mm2)
T = torque
Ʈm = Maximum share