Articles
<![CDATA[Efficiency Analysis of NACA 4412 Semi-Inverse Taper Wind Turbine For Power Plant ]]>
<![CDATA[Sulaiman]]>;
<![CDATA[Asmara Yanto]]>;
<![CDATA[Ikhsan Febryan]]>
<![CDATA[ Jurnal Teknik Mesin Vol 10 No 1 (2020): Jurnal Teknik Mesin Vol.10 No.1 April 2020 ]]>
Publisher : <![CDATA[Lembaga Penelitian dan Pengabdian Masyarakat (LP2M) - ITP ]]>
Show Abstract
|
Download Original
|
Original Source
|
Check in Google Scholar
|
DOI: 10.21063/jtm.2020.v10.i1.46-52
<![CDATA[In this work, a horizontal axis wind turbine (HAWT) are designed and tested to determine turbine efficiency. The wind turbine is built with 3 blades of semi-inverse taper type. This blade is a modification of a type of inverse paper blade that is called semi-inverse taper. This blade is made for moderate wind speeds considering wind in Indonesia. To analyze turbine efficiency, it is necessary to do turbine design and turbine testing stages. From the blade design, the blade radius is 0.9 m. Based on the results of testing and analysis of wind turbine efficiency it can be concluded that the input power and output power are higher with increasing wind speed. However, for the same wind speed, the output power is always smaller than the input power. The increase in input power due to an increase in wind speed is greater than the increase in output power to an increase in wind speed, so the efficiency is lower. The highest wind turbine efficiency was obtained at 84.97% at the lowest wind speed of 5.9 m/s. Whereas at the highest wind speed of 9.3 m/s, turbine efficiency is the lowest at 37.05%.]]>
<![CDATA[Design and Finite Element Analysis of Lawn Mower Machine ]]>
<![CDATA[Rozi Saferi]]>;
<![CDATA[Asmara Yanto]]>;
<![CDATA[Joko Sucipto]]>
<![CDATA[ Jurnal Teknik Mesin Vol 10 No 1 (2020): Jurnal Teknik Mesin Vol.10 No.1 April 2020 ]]>
Publisher : <![CDATA[Lembaga Penelitian dan Pengabdian Masyarakat (LP2M) - ITP ]]>
Show Abstract
|
Download Original
|
Original Source
|
Check in Google Scholar
|
DOI: 10.21063/jtm.2020.v10.i1.60-65
<![CDATA[Technological advances are now being found in everyday, one of them is an android smartphone. Android can be used to control motor speed without using cables with the help of microcontroller, motor driver and bluetooth module. In this study the autors designed and performed static analysis on the framework an android-based lawn mower using Autodesk Inventor. This grass cutting machine consists of several components, that is: framework, battery, microcontroller, motor driver, relay 5v, bluetooth module and others. The design result of an android-based lawn mower have a whole dimension with length = 298.89mm, width = 334.88mm and high = 241.02mm. After static analysis is carried out on the framework obtained results: Displacement minimum 0 mm and displacement maximum 0.0909735 mm, Safety factor minimum 1.93351 and safety factor maximum 15.]]>
<![CDATA[Design, Simulation and Kinematics Analysis of Robot Manipulator with PPRR Joints Configuration ]]>
<![CDATA[Asmara Yanto]]>;
<![CDATA[Ahmad Jeni]]>
<![CDATA[ Jurnal Teknik Mesin Vol 9 No 2 (2019): Jurnal Teknik Mesin Vol.9 No.2 October 2019 ]]>
Publisher : <![CDATA[Lembaga Penelitian dan Pengabdian Masyarakat (LP2M) - ITP ]]>
Show Abstract
|
Download Original
|
Original Source
|
Check in Google Scholar
|
DOI: 10.21063/jtm.2019.v9.i2.65-73
<![CDATA[This research aims to create an innovation in the design of Robot Manipulator with joint configuration in the form of two prismatic movements and two revolute movements (PPRR), serially. The Robot Manipulator design is validated by performing kinematics simulation and analysis of a trajectory. To simulate the movement of this Robot Manipulator, the end-effector Robot Manipulator is equipped with stationery in the form of a marker to follow the trajectory of the block letters. Robot Manipulator consists of four links. Link-1 moves prismatically on a horizontal linear sliding rail system (LSRS) with a rail length of 450 mm. The center point of Link-1 can move from a position of 75 mm to 375 mm in the X-axis direction. The Y-axis parallel links with a length of 80 mm move prismatically on a vertical linear rail system (LSRS) with a rail length of 60 mm. The conditioned link-2 can move from 140 mm to 180 mm in the direction of the Z-axis. Link-3 revolves in the X-Y plane with a range of 0o to 180o. Link-4 revolves in the X-Y plane with a range of 0o to 180o. From the simulation and kinematics analysis of Robot Manipulator with trajectory in the form of ITP block letters it can be concluded that the Robot Manipulator is indicated to be able to follow the trajectory well.]]>
<![CDATA[Kinematic Analysis of A 4-Axis Manipulator Design with 2-Axis Gripper ]]>
<![CDATA[Asmara Yanto]]>;
<![CDATA[Rozi Saferi]]>;
<![CDATA[Anrinal]]>;
<![CDATA[Fikri Azhar]]>
<![CDATA[ Jurnal Teknik Mesin Vol 9 No 1 (2019): Jurnal Teknik Mesin Vol.9 No.1 April 2019 ]]>
Publisher : <![CDATA[Lembaga Penelitian dan Pengabdian Masyarakat (LP2M) - ITP ]]>
Show Abstract
|
Download Original
|
Original Source
|
Check in Google Scholar
|
DOI: 10.21063/jtm.2019.v9.i1.6-14
<![CDATA[The purpose of this work is to analyze the kinematic of a manipulator that was designed to has four revolute movements (R1, R2, R3 and R4) and is equipped with a gripper that has one revolute movement (R) and one prismatic movement (P). The analysis was conducted by varying R1, R2, R3 and R4 of manipulator and R and P of gripper. Kinematic analysis was carried out using the Forward Kinematics method based on DH-Parameters of manipulator and gripper. Manipulator was designed to be consist of 120 mm of Link-1, 200 mm of Link-2, 250 mm of Link-3 and 250 mm of Link-4. Revolute movements range of manipulator was designed for variation of R1, R2, R3 and R4, and with movements range of gripper for variation of R and P. From this work can be concluded that manipulator has 228.5 mm of minimum range radius of end-effector and 547.0 mm of maximum range radius of end-effector.]]>
<![CDATA[Basic Dual-Arm Manipulator Kinematics Using Forward Kinematics Method and Aided by Autodesk Inventor ]]>
<![CDATA[Asmara Yanto]]>
<![CDATA[ Jurnal Teknik Mesin Vol 8 No 2 (2018): Jurnal Teknik Mesin Vol.8 No.2 October 2018 ]]>
Publisher : <![CDATA[Lembaga Penelitian dan Pengabdian Masyarakat (LP2M) - ITP ]]>
Show Abstract
|
Download Original
|
Original Source
|
Check in Google Scholar
|
DOI: 10.21063/jtm.2018.v8.i2.78-87
<![CDATA[This work aims to simulate the kinematics of a basic dual-arm manipulator by using the forward kinematics method and aided by the Autodesk Inventor software. Dual-arm manipulator consists of 7 joints and 6 links. One base link, one shoulder link, two right arm links and two left arm links. Each link is designed with the following length: 310 mm length of link base, 580 mm length of shoulder link, 280 mm length of the first right arm link and left arm link, 222 mm length of the second right arm link and left arm link. The degree of freedom of the dual-arm manipulator is five rotations (5R), namely R1 for base link and shoulder link, R2 for the first left arm link, R3 for the second left arm link, R4 for the first right arm link and R5 for the second right arm link. Parts and assembly of the dual-arm manipulator are designed with Autodesk Inventor. Dual-arm manipulator motions were simulated in two types of trajectory planning. From the simulation for both trajectory planning, the positions of ended left arm and right arm for each step of trajectory planning were visualized and defined.]]>
<![CDATA[METODE SEDERHANA UNTUK MENGETAHUI KARAKTERISTIK DINAMIK MODEL STRUKTUR PADA SKALA LABORATORIUM ]]>
<![CDATA[Asmara Yanto]]>
<![CDATA[ Jurnal Teknik Mesin Vol 5 No 2 (2015): Jurnal Teknik Mesin Vol.5 No.2 October 2015 ]]>
Publisher : <![CDATA[Lembaga Penelitian dan Pengabdian Masyarakat (LP2M) - ITP ]]>
Show Abstract
|
Download Original
|
Original Source
|
Check in Google Scholar
|
DOI: 10.21063/jtm.2015.v5.i2.117-126
<![CDATA[Informasi karakteristik dinamik struktur atau parameter modal diperoleh dengan prosedur modal (theoretical modal analysis atau TMA, experimental modal analysis atau EMA dan operational modal analysis atau OMA). Pada penelitian ini dilakukan suatu cara sederhana yang dapat mendeskripsikan TMA dan EMA terhadap model sistem getaran struktur. Tujuan penelitian ini adalah menentukan salah satu karakteristik dinamik struktur berupa frekuensi pribadi secara teoritis dan eksperimental terhadap sebuah model sistem getaran struktur, yang mana sistem ini tereksitasi oleh gaya dinamik dari ketidakseimbangan massa yang berfrekuensi sebesar frekuensi putaran motor pada sistem. Sistem yang dirancang terdiri dari 3 (tiga) buah massa yaitu massa pada bagian struktur bawah (Massa-1), massa pada bagian struktur tengah (Massa-2) dan massa pada bagian struktur atas (Massa-3). Massa-1 dengan Massa-2 dihubungkan oleh 4 (empat) buah batang penghubung. Begitupun halnya Massa-2 dengan Massa-3. Khusus Massa-1 ditumpu dengan 4 (empat) buah bantalan dan dikondisikan hanya dapat bergetar secara horizontal (searah sumbu-x). Getaran Massa-1 ini dibatasi oleh 2 (dua) buah pegas yang masing-masingnya menghubungkan Massa-1 dengan tumpuan sebelah kanan dan kiri. Pada struktur ini ditempatkan sebuah motor yang dikondisikan mempunyai sistem dengan massa tak seimbang (disk dengan unbalance mass) dengan 3 (tiga) variasi penempatan motor, yaitu penempatan pada Massa-1, Massa-2 dan Massa-3. Penentuan harga frekuensi pribadi secara teoritis dari alat uji model sistem getaran struktur menggunakan metode simulasi numerik dengan perangkat lunak MATLAB. Secara eksperimen, harga frekuensi pribasi ditentukan dengan melakukan pengujian struktur. Pada pengujian ini, putaran motor dikontrol dari putaran ± 100 RPM hingga ± 1800 RPM. Dari simulasi numerik dan eksperimen yang telah dilakukan diperoleh 3 (tiga) buah frekuensi pribadi sistem untuk masing-masing variasi penempatan sistem motor pada sistem. Jika hasil simulasi numerik dibandingkan terhadap eksperimen diperoleh kesalahan yang berkisar antara 4% hingga 18%. Perbedaan hasil simulasi numerik terhadap eksperimen disebabkan karena pada simulasi numerik tidak memperhitungkan gaya gesekan bantalan yang menumpu struktur terhadap tumpuan sistem]]>
<![CDATA[ANALISIS PERILAKU DINAMIK SISTEM POROS-ROTOR 3D ]]>
<![CDATA[Asmara Yanto]]>;
<![CDATA[Rachmat Hidaya]]>
<![CDATA[ Jurnal Teknik Mesin Vol 4 No 2 (2014): Jurnal Teknik Mesin Vol.4 No.2 October 2014 ]]>
Publisher : <![CDATA[Lembaga Penelitian dan Pengabdian Masyarakat (LP2M) - ITP ]]>
Show Abstract
|
Download Original
|
Original Source
|
Check in Google Scholar
|
DOI: 10.21063/jtm.2014.v4.i2.75-83
<![CDATA[In the system of rotating shaft-rotor, vibration problems often occur. Therefore, in order vibration spectrum analysis can be performed with good and safe operating speed limits can be determined properly, then the information on the natural frequency and critical speed of shaft-rotor system must be known well too. Natural frequency of the rotor-shaft system depends on the speed of rotation. In this study we analyzed the dynamic behavior of a shaft-rotor system model by using 3D finite element method and direct method. The analysis was performed to obtain the critical rotation rates and visualizing mode shapes of the shaft-rotor system model 3D. Here, shaft-rotor system model consists of a 3D multi-storey shaft which is divided into 48 elements, two rivet shaft bearings, two disks, each of which is divided into 12 elements. Shaft speed in RPM varied from 0 to 24000 RPM with 100 RPM intervals. For each rotation axis arranged mass matrix, damping matrix, and stiffness matrix systems using the finite element method. The price of natural frequency and mode shape vector price is determined by using the direct method. From the analysis that has been done, the natural frequency obtained 96 forward and 96 backward natural frequency. For 2 pieces of personal frequencies forward and 2 backward the first natural frequency obtained 7 pieces of critical shaft rotation rates. From the visualization mode shape for the first 4 rounds of the critical mode shape obtained at the first natural frequency is equal to the forward mode shape at the first natural frequency and the backward mode shape at the second natural frequency is equal to the forward mode shape at the second natural frequency backward. From the visualization mode shape for 3 rounds last critical mode shape obtained in 2 pieces forward of the first natural frequency and mode shape on the same 2 pieces of the first natural frequency equal backward.]]>
<![CDATA[ANALYSIS OF THE FRF’S CURVE ACCURACY OF TDOF SYSTEM USING LINEAR SWEPT-SINE EXCITATION METHOD ]]>
<![CDATA[Asmara Yanto]]>
<![CDATA[ Jurnal Teknik Mesin Vol 3 No 2 (2013): Jurnal Teknik Mesin Vol.3 No.2 October 2013 ]]>
Publisher : <![CDATA[Lembaga Penelitian dan Pengabdian Masyarakat (LP2M) - ITP ]]>
Show Abstract
|
Download Original
|
Original Source
|
Check in Google Scholar
|
DOI: 10.21063/jtm.2013.v3.i2.32-40
<![CDATA[Pengukuran FRF (Fungsi Respon Frekuensi) memiliki peranan yang sangat penting dalam dinamika struktur. Pengukuran ini biasanya diselenggarakan untuk memperoleh kurva FRF dari sebuah sistem yang diinvestigasi. Dari kurva FRF dapat ditentukan harga frekuensi resonansi dan rasio redaman sistem. Pada pengukuran ini, sistem umumnya dieksitasi dengan palu impak atau shaker. Pengukuran FRF dengan eksitasi shaker sering dilakukan dengan metode eksitasi linear swept-sine. Makalah ini mepaparkan suatu analisa terhadap ketelitian kurva FRF yang diperoleh dari penerapan metode ini pada sebuah Sistem 2-DK (Dua Derajat Kebebasan). Ketelitian kurva FRF ditentukan dengan mengacu kepada persentase kesalahan harga magnitudo FRF dan frekuensi resonansi Sistem 2-DK yang diperoleh terhadap harga teoritiknya. Dari analisa yang dilakukan dapat disimpulkan bahwa ketelitian kurva FRF Sistem 2-DK bergantung kepada durasi eksitasi linear swept-sine yang diterapkan. Apabila eksitasi linear swept-sine diterapkan ke Sistem 2-DK dengan durasi yang lebih lama, maka persentase kesalahan magnitudo FRF dan frekuensi resonansi Sistem 2-DK yang diperoleh lebih kecil dan mendekati harga teoritiknya.]]>
<![CDATA[Design and Structure Analysis of a CNC Laser Engraver Machine ]]>
<![CDATA[Asmara Yanto]]>;
<![CDATA[Anrinal]]>;
<![CDATA[Irfan Mandala Putra]]>
<![CDATA[ Jurnal Teknik Mesin Vol 11 No 2 (2021): Jurnal Teknik Mesin Vol.11 No.2 October 2021 ]]>
Publisher : <![CDATA[Lembaga Penelitian dan Pengabdian Masyarakat (LP2M) - ITP ]]>
Show Abstract
|
Download Original
|
Original Source
|
Check in Google Scholar
|
DOI: 10.21063/jtm.2021.v11.i2.107-116
<![CDATA[This study aims to design a CNC machine to perform the laser engraving process (called the CNC Laser Engraver Machine). The design stage starts from the laser module unit as an input at the design stage of the 3-Axis CNC Machine to drive the laser. The main geometry of the machine is designed referred to the laser position i.e. workspace and laser height with respect to the engraving table. Then the geometry of the Z-Axis unidirectional laser drive unit is determined to assist when adjusting the laser height of the engraving table. Then the geometry of the laser drive unit in the direction of X-Axis and Y-Axis is designed to move on the engraving area, and then the geometry of the engraving table is designed. After the design is complete, the design is validated by analyzing the structure of the machine based on the conditions and workload of the machine to obtain the appropriate dimensions and materials. The design and structure analysis of the CNC Laser Engraver Machine is carried out by using the CAD software. The design results of the CNC Laser Engraver Machine consist of 5 units i.e. Laser Engraver Module Unit, Z-Axis Unit, X-Axis Unit, Y-Axis Unit and Engraving Table Unit which are mounted with a bolt system. This CNC Laser Engraver machine designed has a workspace of 310 mm x 390 mm in the X-Y plane with the laser height in the Z-Axis direction can be adjusted 10 mm to 60 mm above the engraving table. The total dimensions of this CNC Laser Engraver Machine are 585 mm x 533 mm x 350 mm with a total weight about 22 kg.]]>
<![CDATA[Failure Analysis of a Heat Exchanger 212-E9 ]]>
<![CDATA[Dedi Wardianto]]>;
<![CDATA[Karnova Yanel]]>;
<![CDATA[Asmara Yanto]]>
<![CDATA[ Jurnal Teknik Mesin Vol 11 No 2 (2021): Jurnal Teknik Mesin Vol.11 No.2 October 2021 ]]>
Publisher : <![CDATA[Lembaga Penelitian dan Pengabdian Masyarakat (LP2M) - ITP ]]>
Show Abstract
|
Download Original
|
Original Source
|
Check in Google Scholar
|
DOI: 10.21063/jtm.2021.v11.i2.124-131
<![CDATA[Heat Exchanger 212-E9 is one part of the working fluid Debutanizer unit with seawater on inner tubes and H2S on the outside of the tubes. These tubes have failed in the form of leakage. Here the analysis of leakage and the remaining life of the tubes are based on data from the inspection and analysis of general corrosion of the tubes. Part inlet tube erosion-corrosion as well as there are some leaks in the tubes. From the results of inspections in the field, erosion-corrosion of the inlet tube caused by the flow of seawater on the inlet tube containing a solution/coarse material. While the leakage that occurs in tubes due to the H2S concentration is too high, which is equal to 2 mol % H2S. In fact, the recommended H2S concentration is 0.32 mol % H2S. The high level of concentration of H2S is not suitable with the level of material resistance tubes. In the analysis of remaining life obtained maximum corrosion rate in the tubes of 0.2372 mm/year. With the usage time now is 6 year obtained remaining life of 2.5 year again. Referring to the results of the analysis of leakage and remaining life on the tubes is recommended that a filtering of the seawater before entering into the tubes and provide tubes protector on the inlet tube so that tubes are protected from erosion-corrosion, and which is necessary to regulate the level of concentration of H2S Heat Exchanger flowing at the recommended standards.]]>
