Technical Report Con Rod Length, Stroke, Piston Pin Offset, Piston Motion and Dwell in the Lotus-Ford Twin Cam Engine. T. L. Duell.

Size: px
Start display at page:

Download "Technical Report Con Rod Length, Stroke, Piston Pin Offset, Piston Motion and Dwell in the Lotus-Ford Twin Cam Engine. T. L. Duell."

Transcription

1 Technical Report - 1 Con Rod Length, Stroke, Piston Pin Offset, Piston Motion and Dwell in the Lotus-Ford Twin Cam Engine by T. L. Duell May 24 Terry Duell consulting 19 Rylandes Drive, Gladstone Park Victoria 343, Australia ph tduell@planet.net.au

2 24 Terry Duell Published on a RISC OS system using!techwriter Pro+ Figures and diagrams prepared in Gnuplot,!Tau and!draw 2

3 1 Introduction A view has been expressed that Lotus-Ford Twin Cam engines built on the cross flow (Xflow) 711M engine block, using the 77.62mm stroke crankshaft and the 2737E con rod, do not breathe as well at high rpm, as the standard Lotus-Ford Twin Cam engine, which was built on the 12E engine block and used the 72.8mm stroke crankshaft and the 125E con rod. There are various opinions expressed about the importance of con rod length, and many can be found by using "piston dwell" as the search string of an internet search engine. Whilst there is a lot said about the effects of rod length and crank to rod ratios, very few of the opinions appear to be supported by firm data backed by analysis. There appears to be a general view that longer con rods (larger rod length to stroke ratio) will increase piston dwell time, which is said to increases time for combustion and lead to improved torque in the mid to upper rpm range. Some opinions also state that short rods will reduce dwell time and produce good intake and exhaust velocities at low to medium speeds but will cause reduced torque at high rpm This report details a limited investigation into the the geometry of the crank-rod combinations and the motion of the piston, in order to develop some understanding of the magnitude of the effects of changing the crank, rod and other basic engine geometry. The investigation does not aim to address any issues other than those that are directly affected by the crank, rod, and piston geometry. 2 Assumptions A number of assumptions are necessary to make the analysis of the crank, rod and piston geometry manageable. The basic assumptions are; Components are rigid Components have no mass There are no clearances in joints The constant π = Crank angles are measured clockwise from 12 o'clock Clearly, some of these assumptions do not reflect real engines. The calculation of piston displacements, velocities and accelerations at high engine speeds is very complex as con rods stretch and bend, and crankshafts bend and twist. Accounting for all these real world effects would add significant complexity to the problem. The results obtained using these assumptions will indicate relative differences, all other things being equal, and should provide guidance on cause and effect trends. 3

4 3 Basic data Basic data is as shown in Table 1. Engine Bore (mm) Stroke (mm) Con Rod Length (mm) Twin Cam (standard) 711M (X-Flow std) Pin Offset (mm) Rod/Stroke ratio Table 1. Basic engine data The Rod/Stroke ratio is defined as the ratio of the length of the con rod measured from the axis of the piston pin bush to the axis of the big end bearing, to the crankshaft stroke. The crankshaft stroke is twice the crankshaft radius, measured from the axis of the main bearing journal to the axis of the big end bearing journal. 4 The Crank-Rod Model Figure 1 shows the basic geometry for the crank-rod model with pin offset. Analysis of the model is as follows; Fig. 1 The basic crank-rod model, with pin offset 1 A positive offset is to the right of the cylinder axis, as shown in Fig.1. Ref.1 indicates that the Twin Cam piston pin offset is negative. 2 Assumed value 4

5 In Fig. 1, b = R Cos (θ) a = R Sin (θ) d = a o c = L 2 d 2 The piston position = R Cos (θ) + L 2 d 2 = R Cos (θ) + L 2 (a o) 2 = R Cos (θ) + L 2 (R Sin (θ) o) 2 Note that the piston is at top dead center (TDC) position when the crank and rod are in line. The distance moved by the piston from TDC is; g = (L + R) 2 o 2 [R Cos (θ) + L 2 (R Sin (θ) o) 2 ] where R = crank radius = stroke / 2. L = con rod length θ = crank angle af ter vertical o = piston pin of f set The volume, due to piston movement from TDC, can be calculated from g and the cylinder diameter. If the angular velocity of the crank is ω rads/sec, then the linear velocity of the crank pin is Rω, which has a direction normal to the crank. The instantaneous centre of rotation of the con rod at the crankshaft (big-end) is on a line projected along the crank. The velocity of the piston V p will be directed along the axis of the cylinder, and the instantaneous centre of rotation of the small end of the con rod will on a line normal to the axis of the bore through the axis of the piston pin. The center of rotation of the con rod will be at the intersection of those lines projected normal to the direction of the linear velocities, at that instantaneous position. Clearly, the angular velocity of the con rod will be same at both the small and the big-ends, and the velocity of the small end of the con rod will be the same of the piston. Referring to Fig.1, Rω Angular velocity of con rod = e R Rω V p = (f o) e R and e = (c + b) Cos (θ) f = e Sin (θ) Rω Hence V p = e Sin (θ) o e R Note that if N is the engine speed (rpm), then ω = 2πN (rads/sec) 6 5

6 Piston dwell at TDC and at bottom dead centre (BDC) are often mentioned. It should be noted that strictly, there is no dwell period. The piston comes to rest at precisely the crank angle that the crank and rod are in line (TDC and BDC), and is moving at all other crank angles. At crank angles which are very close to the TDC and BDC angles, the piston is moving slowly. It is this slow movement in the vicinity of TDC and BDC that give rise to the term piston dwell. In order that the effects of varying con rod length, stroke and piston pin offset can be assessed, it is necessary to introduce a small piston displacement δ, and then calculate the crank angle range over which the piston remains within that small distance of TDC and BDC. These angle ranges will be the dwell angle. The value of δ used in this investigation is.254 mm (.1"). The basic geometry for the dwell model is shown in Fig. 2. Fig. 2 Basic geometry of the dwell model In Fig. 2a, the crank angle for TDC is established as follows, of f θ = arcsin ( L + R ) 6

7 and the angle for BDC (Fig. 2b) is, of f β = arcsin ( L R ) θ = β + 18 In Fig. 2c the maximum angle at the limit of δ, from TDC, is θ + α + β, and these angles are found as follows, OB 2 = of f 2 + ( L 2 + R 2 of f 2 δ) 2 α = arccos ( R2 + OB 2 L 2 2 R OB ) β = arccos ( (L + R)2 + OB 2 δ 2 2 (L + R) OB ) The minimum angle at the limit of δ from TDC, in Fig. 2c, is θ + β γ. The total dwell angle at TDC, for a piston movement of δ, is, Total TDC angle = θ + α + β + θ + β γ γ = arccos ( R2 + OB 2 L 2 2 R OB ) To find the angles defining the dwell limits at BDC, we use Fig. 2d. of f β = arcsin (L R) 2 of f 2 OD = ( (L R) 2 of f 2 + δ) 2 + of f 2 µ = arccos ( R2 + OD 2 L 2 2 R OD ) β = arccos ( (L R)2 + OD 2 δ 2 2 (L R) OD ) θ = µ β 9 and the max angle θ = 27 θ ϕ = arccos ( R2 + OD 2 L 2 2 R OD ) and the min angle = β + ϕ and the total dwell angle, at BDC, for a piston movement of δ, is (27 θ) β + ϕ The crank stroke, rod length and piston pin offset will each have some effect on the forces and moments on the piston and the axial force on the rod which results in torque on the crank. The geometry for the analysis of the crank moment arm is shown in Fig. 3(a), and the free body diagrams of the piston showing the forces and moments acting on the piston are Fig. 3(b) and Fig. 3(c). 7

8 Fig. 3 Crank moment arm and piston free body diagram Referring to Fig. 3(a), we can establish the crank moment arm (OE), at crank angle θ, as follows; AC = RSin (θ) BC = AC of f Sinβ = BC L RSin (θ) of f β = arcsin ( ) L φ = 9 β θ Cos (φ) = OE R OE = RCos (9 β θ) Fig. 3(b) shows the forces acting on the piston. The gas force ( F g ) acts along the centreline of the cylinder. The thrust force ( F T ) acts normal to the piston, and the friction force ( F ) acts on the thrust face of the piston, parallel to the cylinder axis, and in a direction opposite to the direction of travel of the piston. If we assume that the thrust force acts through the axis of the piston pin, and we transfer the line of action of the gas force and the friction force to the axis of the piston pin, we have the forces and couples as shown in Fig.3(c). 8

9 F R F F = F T = F g F F Cos (β) F g (Tan (µ) Tan (β)) (1 Tan (µ) Tan (β)) = (F g F F ) Tan (β) The couple on the piston due to f riction f orce = M F = F F ( b 2 of f ) The couple on the piston due to gas f orce = M g = F g of f where F g = Gas f orce on piston F = Friction f orce F T = Thrust f orce F R = Axial f orce on rod M g = Couple due to gas f orce M F = Couple due to f riction f orce β = Rod angle to cylinder axis µ = Angle of f riction (Tan (µ) = mu) R = crank radius L = rod length of f = piston pin of f set and the net couple on the piston = M F M g For the purposes of looking at the effect of stroke, rod length and piston pin offset on the torque developed at the crank, we can assume a unit value for the net force on the piston (F g F ), and hence arrive at a corresponding value for F R which is applied to the crank through the distance OE. This analysis provides an insight into the geometric effects without the requirement to know anything about the complexities of the variation of F g with crank angle, or the requirement to quantify the friction between the piston, rings and cylinder wall. If a suitable value of µ and a suitable function or lookup table for F g can be determined for a particular engine, then the more detailed analysis developed above can be used to derive the crank torque-crank angle function for a cycle. 9

10 5 Results Using the relations derived above, the crank angles for TDC and BDC are as shown in table 2. Engine Crank angle TDC (deg) Crank angle BDC (deg) Std TC X-Flow Table 2. TDC and BDC crank angles for Std TC and X-Flow The dwell angles are as shown in table 3. Engine TDC dwell angle (deg) BDC dwell angle (deg) Std TC X-Flow Table 3. Crankshaft angular displacement for piston dwell The effects of con rod length to stroke ratio and piston pin offset on piston dwell are shown in Figs. 4 and 5. Contours of constant dwell angle are shown on the base of the plots. Piston dwell (deg) TDC dwell angle Rod/Stroke ratio Piston pin offset (mm) Fig. 4 Piston dwell (TDC), for varying rod/stroke ratios and pin offsets 1

11 Piston dwell (deg) Rod/Stroke ratio BDC dwell angle Piston pin offset (mm) Fig. 5 Piston dwell (BDC), for varying rod/stroke ratios and pin offsets The effects of con rod length to crank stroke ratio and piston pin offset on the crank torque, with a unit net piston force, for varying crank angle, are shown in Figs 6 and 7. Contours of constant crank torque are shown on the base of the plots. Crank torque (Nmm) Crank torque for 1 N piston force, pin offset=1.16mm Rod/crank ratio Fig. 6 Crank torque for rod/stroke ratio 11

12 Crank torque (Nmm) Crank torque for 1 N piston force, L/Stroke= Fig. 7 Crank torque for pin offset Piston accelerations, for TC and XF, at 6 rpm are shown in Fig XF piston acceleration (m/sec/sec) TC piston acceleration (m/sec/sec) Pin offset (mm) 2 1 Piston acceleration (m/sec/sec) Fig. 8 Piston accelerations TC and XF at 6 rpm Con rod angles, for varying con rod length/stroke ratio, and for varying piston pin offset, are shown in Figs. 9 and 1. Contours of constant rod angle are shown on the base of the plots. 12

13 Rod angle (deg) Con Rod angle, piston pin offset=1.16mm Rod/crank ratio Fig. 9 Con Rod angle for crank angle and rod/crank ratio Rod angle (deg) Con Rod angle, L/Stroke= Fig. 1 Rod angle for crank angle and piston pin offset Piston pin offset (mm) Piston volume and velocity for crank angle, for the TC and XF are shown in Figs. 11 and

14 .3 XF piston displacement (ml) from TDC TC piston displacement (ml) from TDC.25.2 Piston displacement (ml) Fig. 11 Volume change for TC and XF.4.3 XF piston velocity (mm/sec) TC piston velocity (mm/sec).2.1 Piston velocity (mm/sec) Fig. 12 Piston velocity for TC and XF 14

15 6 Discussion The dwell angles (table 3), for a piston displacement of.254mm, are not insignificant, and the X-Flow has slightly smaller dwell angles than the TC. Figs. 4 and 5 show that piston pin offset has a very small effect on dwell angle, relative to the effects of stroke and con rod length. Contours of constant dwell angle are shown on the base of the plot. The detailed data shows that the variation in dwell angle over the range of piston pin offsets used, (-2.32 to 2.32mm) is only approx..7 deg. The maximum dwell angles, for both TDC and BDC, for all rod/stroke ratios examined, occur when the piston pin offset is zero. Piston accelerations near TDC are not noticeably different for the TC and XF (Fig. 8). Where the acceleration is not zero, the acceleration of the XF piston is always higher than that of the TC, for the crank angles shown. Con rod angle (Figs. 9, 1) is affected by both rod/stroke ratio and piston pin offset. Decreasing rod/stroke ratio increases the rod angle, particularly in the region of crank angles of about 4 to 14 degrees. Negative piston pin offsets increase the rod angle, and this effect is also more marked at crank angles nearer 9 deg than nearer 18 degrees. Cylinder volume change with variation in crank angle (Fig. 11), shows the TC and XF very much the same approaching TDC, with the XF showing larger volume change after TDC. Note that the TDC crank angles are not the same (Table 2). Piston velocities near TDC (Fig. 12), shows the same trend as piston accelerations. Where the velocity is not zero, the XF piston acceleration is always higher than that of the TC. The effects of rod length to stroke ratio and piston pin offset on the crank torque for a unit net piston (gas) force, at small crank angles, are shown in Figs. 6 and 7. Contours of crank torque are shown on the base of the plot. Negative piston pin offsets have only a small effect on the crank torque. Rod to stroke ratio has a more noticeable effect. Increasing the crank moment arm and rod angle at low crank angles has potential to improve engine torque, as the cylinder pressure, and hence piston force is very high over the initial stages of the power stroke. The net effect will depend on the rate of increase in the friction force. We can get some idea of the difference that the engine geometry makes to the friction and thrust forces by looking at the ratio of friction force to gas force and the ratio of thrust force to gas force, versus crank angle, for some values of the coefficient of friction. F F F g = F T F g mu tan (β) 1 + mu tan (β) = (1 mu tan (β) ) tan (β) 1 + mu tan (β) where, as before, mu = coef f icient of f riction, β = Rod angle to cylinder axis This approach does not require that we know anything about the magnitude of the gas force, or its variation with crank angle. Results of this analysis, for the TC and XF engine geometries, are shown in Figs. 13 to

16 Piston Friction Force/Gas Force Ratio Ratio of Friction Force to Gas Force, TC Piston/bore friction coefficient Fig. 13 Ratio of Friction force to Gas Force, TC geometry Piston Friction Force/Gas Force Ratio Ratio of Friction Force to Gas Force, XF Piston/bore friction coefficient Fig. 14 Ratio of Friction Force to Gas Force, XF Geometry 16

17 Piston Thrust Force/Gas Force Ratio Ratio of Piston Thrust Force to Gas Force, TC Piston/bore friction coefficient Fig. 15 Ratio of Thrust Force to gas Force, TC Geometry Piston Thrust Force/Gas Force Ratio Ratio of Piston Thrust Force to Gas Force, XF Piston/bore friction coefficient Fig. 16 Ratio of Thrust Force to gas Force, XF Geometry The indications are that the TC friction/gas force ratio is lightly lower than that of the XF, for the same coefficient of friction, and the TC thrust/gas force ratio is also slightly lower than that of the XF, for the same coefficient of friction. This is because of the lower rod angle of the TC, resulting from the larger rod/stroke ratio. 17

18 7 Conclusions A few basic facts can be derived from the analysis, and these are summarised in Table 4. Twin Cam X-Flow Rod/Stroke ratio TDC Dwell 3 (deg) BDC Dwell (deg) TDC Dwell time at 6rpm (sec) BDC Dwell time at 6 rpm (sec) Table 4. Basic data from analysis The effects of changing basic geometric variables, all other things equal, are summarised in Table 5. Change Reduce rod/stroke ratio Reduce piston pin offset 4 Effect Reduces TDC dwell Increases BDC dwell Increases rod angle Increases friction/gas and thrust/gas force ratios Increases crank torque minor increase in crank torque Increases rod angle Reduces piston couple due to gas force (couple= at offset=) Reduces piston couple due to piston friction Maximum dwell angles at piston pin offset= Table 5. Effect of changing basic geometry Note that 'all other things equal' does not always apply. The effects in table 5 are indicative 3 Assuming that the dwell angle is defined by the crank angle range for which a piston remains within.254mm of the TDC or the BDC position. 4 Offset is positive as shown in Fig. 1, reducing includes going from + to - offset 18

19 of general trends only, and in practice may not be achievable due to 'other things no longer being equal'. 19

20 8 References 1. Ford Motor Company of Australia Limited, "Escort Workshop Manual ", March 197 2

Technical Report Lotus Elan Rear Suspension The Effect of Halfshaft Rubber Couplings. T. L. Duell. Prepared for The Elan Factory.

Technical Report Lotus Elan Rear Suspension The Effect of Halfshaft Rubber Couplings. T. L. Duell. Prepared for The Elan Factory. Technical Report - 9 Lotus Elan Rear Suspension The Effect of Halfshaft Rubber Couplings by T. L. Duell Prepared for The Elan Factory May 24 Terry Duell consulting 19 Rylandes Drive, Gladstone Park Victoria

More information

Chapter 15. Inertia Forces in Reciprocating Parts

Chapter 15. Inertia Forces in Reciprocating Parts Chapter 15 Inertia Forces in Reciprocating Parts 2 Approximate Analytical Method for Velocity and Acceleration of the Piston n = Ratio of length of ConRod to radius of crank = l/r 3 Approximate Analytical

More information

Chapter 15. Inertia Forces in Reciprocating Parts

Chapter 15. Inertia Forces in Reciprocating Parts Chapter 15 Inertia Forces in Reciprocating Parts 2 Approximate Analytical Method for Velocity & Acceleration of the Piston n = Ratio of length of ConRod to radius of crank = l/r 3 Approximate Analytical

More information

Part B Problem 1 In a slider crank mechanicsm the length of the crank and connecting rod are 150mm and

Part B Problem 1 In a slider crank mechanicsm the length of the crank and connecting rod are 150mm and SRI RAMAKRISHNA INSTITUTE OF TECHNOLOGY, COIMBATORE-10 (Approved by AICTE, New Delhi Affiliated to Anna University, Chennai) Answer Key Part A 1) D Alembert s Principle It states that the inertia forces

More information

WEEK 4 Dynamics of Machinery

WEEK 4 Dynamics of Machinery WEEK 4 Dynamics of Machinery References Theory of Machines and Mechanisms, J.J.Uicker, G.R.Pennock ve J.E. Shigley, 2003 Prof.Dr.Hasan ÖZTÜRK 1 DYNAMICS OF RECIPROCATING ENGINES Prof.Dr.Hasan ÖZTÜRK The

More information

III B.Tech I Semester Supplementary Examinations, May/June

III B.Tech I Semester Supplementary Examinations, May/June Set No. 1 III B.Tech I Semester Supplementary Examinations, May/June - 2015 1 a) Derive the expression for Gyroscopic Couple? b) A disc with radius of gyration of 60mm and a mass of 4kg is mounted centrally

More information

Balancing of Reciprocating Parts

Balancing of Reciprocating Parts Balancing of Reciprocating Parts We had these forces: Primary and Secondary Unbalanced Forces of Reciprocating Masses m = Mass of the reciprocating parts, l = Length of the connecting rod PC, r = Radius

More information

Analysis of Parametric Studies on the Impact of Piston Velocity Profile On the Performance of a Single Cylinder Diesel Engine

Analysis of Parametric Studies on the Impact of Piston Velocity Profile On the Performance of a Single Cylinder Diesel Engine IOSR Journal of Mechanical and Civil Engineering (IOSR-JMCE) e-issn: 2278-1684,p-ISSN: 2320-334X, Volume 12, Issue 2 Ver. II (Mar - Apr. 2015), PP 81-85 www.iosrjournals.org Analysis of Parametric Studies

More information

1. (a) Discuss various types of Kinematic links with examples. (b) Explain different types of constrained motions with examples.

1. (a) Discuss various types of Kinematic links with examples. (b) Explain different types of constrained motions with examples. Code No: RR310304 Set No. 1 III B.Tech I Semester Supplementary Examinations, February 2007 KINEMATICS OF MACHINERY ( Common to Mechanical Engineering, Mechatronics and Production Engineering) Time: 3

More information

Ledia Bozo Department of Informatics, Tirana University Tirana, ALBANIA,

Ledia Bozo Department of Informatics, Tirana University Tirana, ALBANIA, Impact Of Non Axial Crankshaft Mechanism On The Engines Performance Asllan Hajderi Department of Mechanic and Transport,, Aleksandër Moisiu University Durres Durres ALBANIA; E-mail: ashajderi@yahoo.com

More information

Code No: R Set No. 1

Code No: R Set No. 1 Code No: R05310304 Set No. 1 III B.Tech I Semester Regular Examinations, November 2007 KINEMATICS OF MACHINERY ( Common to Mechanical Engineering, Mechatronics, Production Engineering and Automobile Engineering)

More information

Multi Body Dynamic Analysis of Slider Crank Mechanism to Study the effect of Cylinder Offset

Multi Body Dynamic Analysis of Slider Crank Mechanism to Study the effect of Cylinder Offset Multi Body Dynamic Analysis of Slider Crank Mechanism to Study the effect of Cylinder Offset Vikas Kumar Agarwal Deputy Manager Mahindra Two Wheelers Ltd. MIDC Chinchwad Pune 411019 India Abbreviations:

More information

AT 2303 AUTOMOTIVE POLLUTION AND CONTROL Automobile Engineering Question Bank

AT 2303 AUTOMOTIVE POLLUTION AND CONTROL Automobile Engineering Question Bank AT 2303 AUTOMOTIVE POLLUTION AND CONTROL Automobile Engineering Question Bank UNIT I INTRODUCTION 1. What are the design considerations of a vehicle?(jun 2013) 2..Classify the various types of vehicles.

More information

CH16: Clutches, Brakes, Couplings and Flywheels

CH16: Clutches, Brakes, Couplings and Flywheels CH16: Clutches, Brakes, Couplings and Flywheels These types of elements are associated with rotation and they have in common the function of dissipating, transferring and/or storing rotational energy.

More information

Operating Characteristics

Operating Characteristics Chapter 2 Operating Characteristics 2-1 Engine Parameters 2-22 Work 2-3 Mean Effective Pressure 2-4 Torque and Power 2-5 Dynamometers 2-6 Air-Fuel Ratio and Fuel-Air Ratio 2-7 Specific Fuel Consumption

More information

R10 Set No: 1 ''' ' '' '' '' Code No: R31033

R10 Set No: 1 ''' ' '' '' '' Code No: R31033 R10 Set No: 1 III B.Tech. I Semester Regular and Supplementary Examinations, December - 2013 DYNAMICS OF MACHINERY (Common to Mechanical Engineering and Automobile Engineering) Time: 3 Hours Max Marks:

More information

Features of the Ball Screw

Features of the Ball Screw Features of the Driving Torque One Third of the Sliding Screw With the, balls roll between the screw shaft and the nut to achieve high effi ciency. Its required driving torque is only one third of the

More information

The University of Melbourne Engineering Mechanics

The University of Melbourne Engineering Mechanics The University of Melbourne 436-291 Engineering Mechanics Tutorial Twelve General Plane Motion, Work and Energy Part A (Introductory) 1. (Problem 6/78 from Meriam and Kraige - Dynamics) Above the earth

More information

Theory of Machines. CH-1: Fundamentals and type of Mechanisms

Theory of Machines. CH-1: Fundamentals and type of Mechanisms CH-1: Fundamentals and type of Mechanisms 1. Define kinematic link and kinematic chain. 2. Enlist the types of constrained motion. Draw a label sketch of any one. 3. Define (1) Mechanism (2) Inversion

More information

ME6401 KINEMATICS OF MACHINERY UNIT- I (Basics of Mechanism)

ME6401 KINEMATICS OF MACHINERY UNIT- I (Basics of Mechanism) ME6401 KINEMATICS OF MACHINERY UNIT- I (Basics of Mechanism) 1) Define resistant body. 2) Define Link or Element 3) Differentiate Machine and Structure 4) Define Kinematic Pair. 5) Define Kinematic Chain.

More information

B.TECH III Year I Semester (R09) Regular & Supplementary Examinations November 2012 DYNAMICS OF MACHINERY

B.TECH III Year I Semester (R09) Regular & Supplementary Examinations November 2012 DYNAMICS OF MACHINERY 1 B.TECH III Year I Semester (R09) Regular & Supplementary Examinations November 2012 DYNAMICS OF MACHINERY (Mechanical Engineering) Time: 3 hours Max. Marks: 70 Answer any FIVE questions All questions

More information

Development, Implementation, and Validation of a Fuel Impingement Model for Direct Injected Fuels with High Enthalpy of Vaporization

Development, Implementation, and Validation of a Fuel Impingement Model for Direct Injected Fuels with High Enthalpy of Vaporization Development, Implementation, and Validation of a Fuel Impingement Model for Direct Injected Fuels with High Enthalpy of Vaporization (SAE Paper- 2009-01-0306) Craig D. Marriott PE, Matthew A. Wiles PE,

More information

WEAR PROFILE OF THE CYLINDER LINER IN A MOTOR TRUCK DIESEL ENGINE

WEAR PROFILE OF THE CYLINDER LINER IN A MOTOR TRUCK DIESEL ENGINE Journal of KONES Powertrain and Transport, Vol.14, No. 4 27 WEAR PROFILE OF THE CYLINDER LINER IN A MOTOR TRUCK DIESEL ENGINE Grzegorz Kosza ka, Andrzej Niewczas Lublin University of Technology Dept. of

More information

PREDICTION OF PISTON SLAP OF IC ENGINE USING FEA BY VARYING GAS PRESSURE

PREDICTION OF PISTON SLAP OF IC ENGINE USING FEA BY VARYING GAS PRESSURE PREDICTION OF PISTON SLAP OF IC ENGINE USING FEA BY VARYING GAS PRESSURE V. S. Konnur Department of Mechanical Engineering, BLDEA s Engineering College, Bijapur, Karnataka, (India) ABSTRACT The automotive

More information

Hours / 100 Marks Seat No.

Hours / 100 Marks Seat No. 17412 16117 3 Hours / 100 Seat No. Instructions (1) All Questions are Compulsory. (2) Answer each next main Question on a new page. (3) Illustrate your answers with neat sketches wherever necessary. (4)

More information

Studying the Positioning Accuracy

Studying the Positioning Accuracy Ball Screw Studying the Positioning Accuracy Causes of Error in the Positioning Accuracy Point of Selection Studying the Positioning Accuracy The causes of error in the positioning accuracy include the

More information

Internal Combustion Engines

Internal Combustion Engines Friction & Lubrication Lecture 1 1 Outline In this lecture we will discuss the following: Engine friction losses. Piston arrangement losses. Measurement of friction losses. Engine lubrication systems.

More information

SHOCK DYNAMOMETER: WHERE THE GRAPHS COME FROM

SHOCK DYNAMOMETER: WHERE THE GRAPHS COME FROM SHOCK DYNAMOMETER: WHERE THE GRAPHS COME FROM Dampers are the hot race car component of the 90s. The two racing topics that were hot in the 80s, suspension geometry and data acquisition, have been absorbed

More information

Simulation Method of Hydraulic Confined Piston Engine

Simulation Method of Hydraulic Confined Piston Engine 5th International Conference on Advanced Design and Manufacturing Engineering (ICADME 2015) Simulation Method of Hydraulic Confined Piston Engine JIAO Yuqin 1, a, ZHANG Hongxin 1,b * and XU Wei 1,c 1 Electromechanic

More information

THEORY OF MACHINES FRICTION CLUTCHES

THEORY OF MACHINES FRICTION CLUTCHES THEORY OF MACHINES FRICTION CLUTCHES Introduction A friction clutch has its principal application in the transmission of power of shafts and machines which must be started and stopped frequently. Its application

More information

Design, Analysis &Optimization of Crankshaft Using CAE

Design, Analysis &Optimization of Crankshaft Using CAE Design, Analysis &Optimization of Crankshaft Using CAE Dhekale Harshada 1, Jagtap Ashwini 2, Lomte Madhura 3, Yadav Priyanka 4 1,2,3,4 Government College of Engineering and Research Awasari, Department

More information

DHANALAKSHMI COLLEGE OF ENGINEERING

DHANALAKSHMI COLLEGE OF ENGINEERING DHANALAKSHMI COLLEGE OF ENGINEERING (Dr.VPR Nagar, Manimangalam, Tambaram) Chennai - 601 301 DEPARTMENT OF MECHANICAL ENGINEERING III YEAR MECHANICAL - VI SEMESTER ME 6601 DESIGN OF TRANSMISSION SYSTEMS

More information

MODIFICATION OF SLIDER CRANK MECHANISM AND STUDY OF THE CURVES ASSOCIATED WITH IT

MODIFICATION OF SLIDER CRANK MECHANISM AND STUDY OF THE CURVES ASSOCIATED WITH IT MODIFICATION OF SLIDER CRANK MECHANISM AND STUDY OF THE CURVES ASSOCIATED WITH IT Samiron Neog 1, Deep Singh 2, Prajnyan Ballav Goswami 3 1,2,3 Student,B. Tech.,Mechanical, Dibrugarh University Institute

More information

Kul Internal Combustion Engine Technology. Definition & Classification, Characteristics 2015 Basshuysen 1,2,3,4,5

Kul Internal Combustion Engine Technology. Definition & Classification, Characteristics 2015 Basshuysen 1,2,3,4,5 Kul-14.4100 Internal Combustion Engine Technology Definition & Classification, Characteristics 2015 Basshuysen 1,2,3,4,5 Definitions Combustion engines convert the chemical energy of fuel to mechanical

More information

NEW CONCEPT OF A ROCKER ENGINE KINEMATIC ANALYSIS

NEW CONCEPT OF A ROCKER ENGINE KINEMATIC ANALYSIS Journal of KONES Powertrain and Transport, Vol. 19, No. 3 2012 NEW CONCEPT OF A ROCKER ENGINE KINEMATIC ANALYSIS Miros aw Szymkowiak Kochanowskiego Street 13, 64-100 Leszno, Poland e-mail: szymkowiak@op.pl

More information

Rotational Kinematics and Dynamics Review

Rotational Kinematics and Dynamics Review Rotational Kinematics and Dynamics Review 1. The Earth takes slightly less than one day to complete one rotation about the axis passing through its poles. The actual time is 8.616 10 4 s. Given this information,

More information

UNDERSTANDING ROD RATIOS

UNDERSTANDING ROD RATIOS UNDERSTANDING ROD RATIOS By Larry Carley, Technical Editor lcarley@babcox.com Performance engine builders are always looking at changes they can make that will give their engine an edge over the competition.

More information

The Sommerfeld number is also a dimensionless parameter used extensively in the design of

The Sommerfeld number is also a dimensionless parameter used extensively in the design of Critical Pressure of the Journal Bearing The pressure at which the oil film breaks down so that metal to metal contact begins, is known as critical pressure or the minimum operating pressure of the bearing.

More information

FIRSTRANKER. 2. (a) Distinguish (by neat sketches) betweenpeaucellier mechanism and Hart mechanism.

FIRSTRANKER. 2. (a) Distinguish (by neat sketches) betweenpeaucellier mechanism and Hart mechanism. Code No: 07A51404 R07 Set No. 2 IIIB.Tech I Semester Examinations,May 2011 KINEMATICS OF MACHINERY Mechatronics Time: 3 hours Max Marks: 80 Answer any FIVE Questions All Questions carry equal marks 1.

More information

Lab #3 - Slider-Crank Lab

Lab #3 - Slider-Crank Lab Lab #3 - Slider-Crank Lab Revised March 19, 2012 INTRODUCTION In this lab we look at the kinematics of some mechanisms which convert rotary motion into oscillating linear motion and vice-versa. In kinematics

More information

Bevel Gears. Fig.(1) Bevel gears

Bevel Gears. Fig.(1) Bevel gears Bevel Gears Bevel gears are cut on conical blanks to be used to transmit motion between intersecting shafts. The simplest bevel gear type is the straighttooth bevel gear or straight bevel gear as can be

More information

Motional emf. as long as the velocity, field, and length are mutually perpendicular.

Motional emf. as long as the velocity, field, and length are mutually perpendicular. Motional emf Motional emf is the voltage induced across a conductor moving through a magnetic field. If a metal rod of length L moves at velocity v through a magnetic field B, the motional emf is: ε =

More information

DEVELOPMENT OF A CONTROL MODEL FOR A FOUR WHEEL MECANUM VEHICLE. M. de Villiers 1, Prof. G. Bright 2

DEVELOPMENT OF A CONTROL MODEL FOR A FOUR WHEEL MECANUM VEHICLE. M. de Villiers 1, Prof. G. Bright 2 de Villiers Page 1 of 10 DEVELOPMENT OF A CONTROL MODEL FOR A FOUR WHEEL MECANUM VEHICLE M. de Villiers 1, Prof. G. Bright 2 1 Council for Scientific and Industrial Research Pretoria, South Africa e-mail1:

More information

VALLIAMMAI ENGINEERING COLLEGE DEPARTMENT OF MECHANICAL ENGINEERING ME6401- KINEMATICS OF MACHINERY QUESTION BANK PART-A Unit 1-BASICS OF MECHANISMS 1. Define degrees of freedom. BT1 2. Describe spatial

More information

DEVELOPMENT OF COMPRESSED AIR POWERED ENGINE SYSTEM BASED ON SUBARU EA71 MODEL CHEN RUI

DEVELOPMENT OF COMPRESSED AIR POWERED ENGINE SYSTEM BASED ON SUBARU EA71 MODEL CHEN RUI DEVELOPMENT OF COMPRESSED AIR POWERED ENGINE SYSTEM BASED ON SUBARU EA71 MODEL CHEN RUI A project report submitted in partial fulfillment of the requirements for the award of the degree of Bachelor of

More information

Code No: R Set No. 1

Code No: R Set No. 1 Code No: R05222106 Set No. 1 II B.Tech II Semester Supplimentary Examinations, Aug/Sep 2007 MECHANISMS AND MECHANICAL DESIGN (Aeronautical Engineering) Time: 3 hours Max Marks: 80 Answer any FIVE Questions

More information

Gearless Power Transmission-Offset Parallel Shaft Coupling

Gearless Power Transmission-Offset Parallel Shaft Coupling Gearless Power Transmission-Offset Parallel Shaft Coupling Mahantesh Tanodi 1, S. B. Yapalaparvi 2, Anand. C. Mattikalli 3, D. N. Inamdar 2, G. V. Chiniwalar 2 1 PG Scholar, Department of Mechanical Engineering,

More information

KINEMATICS OF MACHINARY UBMC302 QUESTION BANK UNIT-I BASICS OF MECHANISMS PART-A

KINEMATICS OF MACHINARY UBMC302 QUESTION BANK UNIT-I BASICS OF MECHANISMS PART-A KINEMATICS OF MACHINARY UBMC302 QUESTION BANK UNIT-I BASICS OF MECHANISMS PART-A 1. Define the term Kinematic link. 2. Classify kinematic links. 3. What is Mechanism? 4. Define the terms Kinematic pair.

More information

Design and Analysis of Four Cylinder Diesel Engine Balancer Shaft

Design and Analysis of Four Cylinder Diesel Engine Balancer Shaft Design and Analysis of Four Cylinder Diesel Engine Balancer Shaft Gopal Kumar Kumhar M. Tech CAD/CAM VIT University Vandalur - Kelambakkam Road, Chennai, Tamil Nadu-600048 Shakti Kumar Singh Chief Manager

More information

B.Tech. MECHANICAL ENGINEERING (BTMEVI) Term-End Examination December, 2012 BIMEE-007 : ADVANCED DYNAMICS OF MACHINE

B.Tech. MECHANICAL ENGINEERING (BTMEVI) Term-End Examination December, 2012 BIMEE-007 : ADVANCED DYNAMICS OF MACHINE No. of Printed Pages : 5 BIMEE-007 B.Tech. MECHANICAL ENGINEERING (BTMEVI) Term-End Examination 01601 December, 2012 BIMEE-007 : ADVANCED DYNAMICS OF MACHINE Time : 3 hours Maximum Marks : 70 Note : Attempt

More information

California State University, Bakersfield. Signals and Systems. Kristin Koehler. California State University, Bakersfield Lecture 4 July 18 th, 2013

California State University, Bakersfield. Signals and Systems. Kristin Koehler. California State University, Bakersfield Lecture 4 July 18 th, 2013 Kristin Koehler California State University, Bakersfield Lecture 4 July 18 th, 2013 1 Outline Internal combustion engines 2 stroke combustion engines 4 stroke combustion engines Diesel engines 2 Consists

More information

A Novel Device to Measure Instantaneous Swept Volume of Internal Combustion Engines

A Novel Device to Measure Instantaneous Swept Volume of Internal Combustion Engines Global Journal of Researches in Engineering Vol. 10 Issue 7 (Ver1.0), December 2010 P a g e 47 A Novel Device to Measure Instantaneous Swept Volume of Internal Combustion Engines MURUGAN. R. GJRE -A Classification

More information

Analytical method of finding velocity and acceleration in slider crank mechanism

Analytical method of finding velocity and acceleration in slider crank mechanism Analytical method of finding velocity and acceleration in slider crank mechanism Formulae for Analytical method of finding velocity and acceleration in slider crank mechanism Ratio n = connecting rod length

More information

Comparative Study Of Four Stroke Diesel And Petrol Engine.

Comparative Study Of Four Stroke Diesel And Petrol Engine. Comparative Study Of Four Stroke Diesel And Petrol Engine. Aim: To study the construction and working of 4- stroke petrol / diesel engine. Theory: A machine or device which derives heat from the combustion

More information

Load Analysis and Multi Body Dynamics Analysis of Connecting Rod in Single Cylinder 4 Stroke Engine

Load Analysis and Multi Body Dynamics Analysis of Connecting Rod in Single Cylinder 4 Stroke Engine IJSRD - International Journal for Scientific Research & Development Vol. 3, Issue 08, 2015 ISSN (online): 2321-0613 Load Analysis and Multi Body Dynamics Analysis of Connecting Rod in Single Cylinder 4

More information

Application of ABAQUS to Analyzing Shrink Fitting Process of Semi Built-up Type Marine Engine Crankshaft

Application of ABAQUS to Analyzing Shrink Fitting Process of Semi Built-up Type Marine Engine Crankshaft Application of ABAQUS to Analyzing Shrink Fitting Process of Semi Built-up Type Marine Engine Crankshaft Jae-Cheol Kim, Dong-Kwon Kim, Young-Duk Kim, and Dong-Young Kim System Technology Research Team,

More information

Design and Stress Analysis of Crankshaft for Single Cylinder 4-Stroke Diesel Engine

Design and Stress Analysis of Crankshaft for Single Cylinder 4-Stroke Diesel Engine Design and Stress Analysis of Crankshaft for Single Cylinder 4-Stroke Diesel Engine Amit Solanki #1, Jaydeepsinh Dodiya #2, # Mechanical Engg.Deptt, C.U.Shah University, Wadhwan city, Gujarat, INDIA Abstract

More information

DEPARTMENT OF MECHANICAL ENGINEERING ME6401- KINEMATICS OF MACHINERY QUESTION BANK Part-A Unit 1-BASICS OF MECHANISMS 1. Define degrees of freedom. 2. What is meant by spatial mechanism? 3. Classify the

More information

Bevel Gears n A Textbook of Machine Design

Bevel Gears n A Textbook of Machine Design 080 n A Textbook of Machine Design C H A P T E R 30 Bevel Gears. Introduction.. Classification of Bevel Gears. 3. Terms used in Bevel Gears. 4. Determination of Pitch Angle for Bevel Gears. 5. Proportions

More information

Unit WorkBook 4 Level 4 ENG U13 Fundamentals of Thermodynamics and Heat Engines UniCourse Ltd. All Rights Reserved. Sample

Unit WorkBook 4 Level 4 ENG U13 Fundamentals of Thermodynamics and Heat Engines UniCourse Ltd. All Rights Reserved. Sample Pearson BTEC Levels 4 Higher Nationals in Engineering (RQF) Unit 13: Fundamentals of Thermodynamics and Heat Engines Unit Workbook 4 in a series of 4 for this unit Learning Outcome 4 Internal Combustion

More information

A Low Friction Thrust Bearing for Reciprocating Compressors

A Low Friction Thrust Bearing for Reciprocating Compressors Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering A Low Friction Thrust Bearing for Reciprocating Compressors Shuhei Nagata shuhei.nagata.wq@hitachi.com

More information

Driven Damped Harmonic Oscillations

Driven Damped Harmonic Oscillations Driven Damped Harmonic Oscillations EQUIPMENT INCLUDED: Rotary Motion Sensors CI-6538 1 Mechanical Oscillator/Driver ME-8750 1 Chaos Accessory CI-6689A 1 Large Rod Stand ME-8735 10-cm Long Steel Rods ME-8741

More information

2. a) What is pantograph? What are its uses? b) Prove that the peaucellier mechanism generates a straight-line motion. (5M+10M)

2. a) What is pantograph? What are its uses? b) Prove that the peaucellier mechanism generates a straight-line motion. (5M+10M) Code No: R22032 R10 SET - 1 1. a) Define the following terms? i) Link ii) Kinematic pair iii) Degrees of freedom b) What are the inversions of double slider crank chain? Describe any two with neat sketches.

More information

Seals Stretch Running Friction Friction Break-Out Friction. Build With The Best!

Seals Stretch Running Friction Friction Break-Out Friction. Build With The Best! squeeze, min. = 0.0035 with adverse tolerance build-up. If the O-ring is made in a compound that will shrink in the fluid, the minimum possible squeeze under adverse conditions then must be at least.076

More information

LEG PROTECTION FOR MOTORCYCLISTS. B. P. Chinn T.R.R.L. M.A. Macaulay Brunel University

LEG PROTECTION FOR MOTORCYCLISTS. B. P. Chinn T.R.R.L. M.A. Macaulay Brunel University LEG PROTECTION FOR MOTORCYCLISTS B. P. Chinn T.R.R.L. M.A. Macaulay Brunel University 1. Introduction A number of earlier papers by Chinn and Macaulay (1), Chinn, Hopes and Macaulay (2) and Macaulay and

More information

Drag Factors in Spins and on Hills

Drag Factors in Spins and on Hills Drag Factors in Spins and on Hills John Daily Jackson Hole Scientific Investigations, Inc. Box 2206 Jackson, WY 83001 (307) 733-4559 jhsi@rmisp.com Drag Factor Adjustment Adjusting the drag factor for

More information

Transmission Error in Screw Compressor Rotors

Transmission Error in Screw Compressor Rotors Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 2008 Transmission Error in Screw Compressor Rotors Jack Sauls Trane Follow this and additional

More information

Gas exchange process for IC-engines: poppet valves, valve timing and variable valve actuation

Gas exchange process for IC-engines: poppet valves, valve timing and variable valve actuation Gas exchange process for IC-engines: poppet valves, valve timing and variable valve actuation Topics Analysis of the main parameters influencing the volumetric efficiency in IC engines: - Valves and valve

More information

Active Suspensions For Tracked Vehicles

Active Suspensions For Tracked Vehicles Active Suspensions For Tracked Vehicles Y.G.Srinivasa, P. V. Manivannan 1, Rajesh K 2 and Sanjay goyal 2 Precision Engineering and Instrumentation Lab Indian Institute of Technology Madras Chennai 1 PEIL

More information

Influence of Internal Combustion Engine Parameters on Gas Leakage through the Piston Rings Area

Influence of Internal Combustion Engine Parameters on Gas Leakage through the Piston Rings Area Modern Mechanical Engineering, 2017, 7, 27-33 http://www.scirp.org/journal/mme ISSN Online: 2164-0181 ISSN Print: 2164-0165 Influence of Internal Combustion Engine Parameters on Gas Leakage through the

More information

Dependence of Shaft Stiffness on the Crack Location

Dependence of Shaft Stiffness on the Crack Location Dependence of Shaft Stiffness on the Crack Location H. M. Mobarak, Helen Wu, Chunhui Yang Abstract In this study, an analytical model is developed to study crack breathing behavior under the effect of

More information

EEN-E2002 Internal Combustion Definitions and Characteristics, lecture 3. January 2017, Martti Larmi

EEN-E2002 Internal Combustion Definitions and Characteristics, lecture 3. January 2017, Martti Larmi EEN-E2002 Internal Combustion Definitions and Characteristics, lecture 3 January 2017, Martti Larmi Textbooks on Internal Combustion Internal combustion engine handbook : basics, components, systems, and

More information

Moments. It doesn t fall because of the presence of a counter balance weight on the right-hand side. The boom is therefore balanced.

Moments. It doesn t fall because of the presence of a counter balance weight on the right-hand side. The boom is therefore balanced. Moments The crane in the image below looks unstable, as though it should topple over. There appears to be too much of the boom on the left-hand side of the tower. It doesn t fall because of the presence

More information

TECHNICAL NOTE. NADS Vehicle Dynamics Typical Modeling Data. Document ID: N Author(s): Chris Schwarz Date: August 2006

TECHNICAL NOTE. NADS Vehicle Dynamics Typical Modeling Data. Document ID: N Author(s): Chris Schwarz Date: August 2006 TECHNICAL NOTE NADS Vehicle Dynamics Typical Modeling Data Document ID: N06-017 Author(s): Chris Schwarz Date: August 2006 National Advanced Driving Simulator 2401 Oakdale Blvd. Iowa City, IA 52242-5003

More information

Changes in direction.! Using pulleys with belts

Changes in direction.! Using pulleys with belts Mechanisms Changes in direction! Using pulleys with belts Changes in direction! Using friction wheels Changes in direction! Using gears Worm drive! Reduces the speed! It is non-reversible Worm drive! Multiple

More information

Simple Gears and Transmission

Simple Gears and Transmission Simple Gears and Transmission Simple Gears and Transmission page: of 4 How can transmissions be designed so that they provide the force, speed and direction required and how efficient will the design be?

More information

VEHICLE ANTI-ROLL BAR ANALYZED USING FEA TOOL ANSYS

VEHICLE ANTI-ROLL BAR ANALYZED USING FEA TOOL ANSYS VEHICLE ANTI-ROLL BAR ANALYZED USING FEA TOOL ANSYS P. M. Bora 1, Dr. P. K. Sharma 2 1 M. Tech. Student,NIIST, Bhopal(India) 2 Professor & HOD,NIIST, Bhopal(India) ABSTRACT The aim of this paper is to

More information

Flywheel. 776 A Textbook of Machine Design

Flywheel. 776 A Textbook of Machine Design 776 A Textbook of Machine Design C H A P T E R Flywheel 1. Introduction.. Coefficient of Fluctuation of Speed. 3. Fluctuation of Energy. 4. Maximum Fluctuation of Energy. 5. Coefficient of Fluctuation

More information

Improvement of Vehicle Dynamics by Right-and-Left Torque Vectoring System in Various Drivetrains x

Improvement of Vehicle Dynamics by Right-and-Left Torque Vectoring System in Various Drivetrains x Improvement of Vehicle Dynamics by Right-and-Left Torque Vectoring System in Various Drivetrains x Kaoru SAWASE* Yuichi USHIRODA* Abstract This paper describes the verification by calculation of vehicle

More information

SUCCESSFUL DIESEL COLD START THROUGH PROPER PILOT INJECTION PARAMETERS SELECTION. Aleksey Marchuk, Georgiy Kuharenok, Aleksandr Petruchenko

SUCCESSFUL DIESEL COLD START THROUGH PROPER PILOT INJECTION PARAMETERS SELECTION. Aleksey Marchuk, Georgiy Kuharenok, Aleksandr Petruchenko SUCCESSFUL DIESEL COLD START THROUGH PROPER PILOT INJECTION PARAMETERS SELECTION Aleksey Marchuk, Georgiy Kuharenok, Aleksandr Petruchenko Robert Bosch Company, Germany Belarussian National Technical Universitry,

More information

Advantages and Disadvantages of Rolling Contact Bearings Over Sliding Contact Bearings

Advantages and Disadvantages of Rolling Contact Bearings Over Sliding Contact Bearings Advantages and Disadvantages of Rolling Contact Bearings Over Sliding Contact Bearings Advantages 1. Low starting and running friction except at very high speeds. 2. Ability to withstand momentary shock

More information

UNIT - III GYROSCOPE

UNIT - III GYROSCOPE UNIT - III GYROSCOPE Introduction 1When a body moves along a curved path, a force in the direction of centripetal acceleration (centripetal force ) has to be applied externally This external force is known

More information

UNIT -I. Ans: They are specified by the no. of strands & the no. of wires in each strand.

UNIT -I. Ans: They are specified by the no. of strands & the no. of wires in each strand. VETRI VINAYAHA COLLEGE OF ENGINEERING AND TECHNOLOGY, THOTTIAM, NAMAKKAL-621215. DEPARTMENT OF MECHANICAL ENGINEERING SIXTH SEMESTER / III YEAR ME6601 DESIGN OF TRANSMISSION SYSTEM (Regulation-2013) UNIT

More information

FEM ANALYSIS OF CONNECTING ROD FOR STATIONARY ENGINE. Republic

FEM ANALYSIS OF CONNECTING ROD FOR STATIONARY ENGINE. Republic FEM ANALYSIS OF CONNECTING ROD FOR STATIONARY ENGINE P. Brabec, P. Kefurt, C. Scholz, R. Voženílek Technical University of Liberec, Hálkova, Liberec, Czech Republic BEZ MOTORY, a.s., Plotiště nad Labem,

More information

Ball Screw. General Catalog A-661

Ball Screw. General Catalog A-661 General Catalog A-661 Features and Types Ball Screw Features of the Ball Screw Driving Torque One Third of the Sliding Screw With the Ball Screw, balls roll between the screw shaft and the nut to achieve

More information

PHYA5/2C. General Certificate of Education Advanced Level Examination June Section B. Monday 18 June am to am (JUN12PHYA52C01)

PHYA5/2C. General Certificate of Education Advanced Level Examination June Section B. Monday 18 June am to am (JUN12PHYA52C01) Centre Number Surname Candidate Number For Examinerʼs Use Other Names Candidate Signature Examinerʼs Initials General Certificate of Education Advanced Level Examination June 2012 Question 1 2 Mark Physics

More information

A New Device to Measure Instantaneous Swept Volume of Reciprocating Machines/Compressors

A New Device to Measure Instantaneous Swept Volume of Reciprocating Machines/Compressors Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 2004 A New Device to Measure Instantaneous Swept Volume of Reciprocating Machines/Compressors

More information

The Multibody Systems Approach to Vehicle Dynamics

The Multibody Systems Approach to Vehicle Dynamics The Multibody Systems Approach to Vehicle Dynamics A Short Course Lecture 4 Tyre Characteristics Professor Mike Blundell Phd, MSc, BSc (Hons), FIMechE, CEng Course Agenda Day 1 Lecture 1 Introduction to

More information

(12) United States Patent Moteki et al.

(12) United States Patent Moteki et al. (12) United States Patent Moteki et al. US006505582B2 (10) Patent N0.: (45) Date of Patent: US 6,505,582 B2 Jan. 14, 2003 (54) VARIABLE COMPRESSION RATIO MECHANISM OF RECIPROCATING INTERNAL COMBUSTION

More information

Precision Degree Wheel Kit

Precision Degree Wheel Kit 555-81621 Precision Degree Wheel Kit Instruction Booklet Instructions for 81621 Camshaft Degree Kit Thank you for purchasing the Jegs Camshaft Degree Kit. Please follow these detailed instructions to properly

More information

ACTUAL CYCLE. Actual engine cycle

ACTUAL CYCLE. Actual engine cycle 1 ACTUAL CYCLE Actual engine cycle Introduction 2 Ideal Gas Cycle (Air Standard Cycle) Idealized processes Idealize working Fluid Fuel-Air Cycle Idealized Processes Accurate Working Fluid Model Actual

More information

Internal Combustion Engine

Internal Combustion Engine Internal Combustion Engine 1. A 9-cylinder, 4-stroke cycle, radial SI engine operates at 900rpm. Calculate: (1) How often ignition occurs, in degrees of engine rev. (2) How many power strokes per rev.

More information

ADVANCED STEEL OFFERS AUTOMAKERS AGGRESSIVE ENGINE DOWNSIZING

ADVANCED STEEL OFFERS AUTOMAKERS AGGRESSIVE ENGINE DOWNSIZING ADVANCED STEEL OFFERS AUTOMAKERS AGGRESSIVE ENGINE DOWNSIZING Andy Schmitter Nucor Corporation Background and Scope The Bar Applications Group (BAG),a committee of the Steel Market Development Institute

More information

10/29/2018. Chapter 16. Turning Moment Diagrams and Flywheel. Mohammad Suliman Abuhaiba, Ph.D., PE

10/29/2018. Chapter 16. Turning Moment Diagrams and Flywheel. Mohammad Suliman Abuhaiba, Ph.D., PE 1 Chapter 16 Turning Moment Diagrams and Flywheel 2 Turning moment diagram (TMD) graphical representation of turning moment or crank-effort for various positions of the crank 3 Turning Moment Diagram for

More information

12/25/2015. Chapter 20. Cams. Mohammad Suliman Abuhiba, Ph.D., PE

12/25/2015. Chapter 20. Cams. Mohammad Suliman Abuhiba, Ph.D., PE Chapter 20 Cams 1 2 Introduction A cam: a rotating machine element which gives reciprocating or oscillating motion to another element (follower) Cam & follower have a line constitute a higher pair. of

More information

I.C ENGINES. CLASSIFICATION I.C Engines are classified according to:

I.C ENGINES. CLASSIFICATION I.C Engines are classified according to: I.C ENGINES An internal combustion engine is most popularly known as I.C. engine, is a heat engine which converts the heat energy released by the combustion of the fuel taking place inside the engine cylinder

More information

LM Guide Actuator KR. For details, visit THK at CATALOG No E. Product information is updated regularly on the THK website.

LM Guide Actuator KR. For details, visit THK at  CATALOG No E. Product information is updated regularly on the THK website. LM Guide Actuator KR For details, visit THK at www.thk.com Product information is updated regularly on the THK website. CATALOG No.209-10E Integrated LM Guide and all Screw High-rigidity / High-precision

More information

...components in motion. Miniature Linear Guideways

...components in motion. Miniature Linear Guideways ...components in motion Miniature Linear Introduction Miniature linear guideway systems are widely used throughout industry for precise, compact applications. Precise and Stainless The gothic arch shape

More information

FRONTAL OFF SET COLLISION

FRONTAL OFF SET COLLISION FRONTAL OFF SET COLLISION MARC1 SOLUTIONS Rudy Limpert Short Paper PCB2 2014 www.pcbrakeinc.com 1 1.0. Introduction A crash-test-on- paper is an analysis using the forward method where impact conditions

More information

A study on the application of tripod joints to transmit the driving torque of axial piston hydraulic motor

A study on the application of tripod joints to transmit the driving torque of axial piston hydraulic motor A study on the application of tripod joints to transmit the driving torque of axial piston hydraulic motor Youna-Boa HAM*, Sung-Dona KIM** *Senior Researcher, Department of Advanced Industrial Technology

More information