Q: Fuel ignition quality — reference fuels for cetane number In the conventional cetane rating scale for diesel fuels, which pair of reference fuels defines the ends of the scale used to match ignition delay in a standardized engine?

Introduction / Context: Cetane number is the ignition quality index for diesel fuels, analogous to octane number for petrol. It is defined by comparing ignition delay to that of blends of standard reference fuels in a test engine under specified conditions. Given Data / Assumptions: Cetane number scale based on ignition delay time. Reference fuels establish fixed ignition characteristics for calibration. Concept / Approach: Traditionally, the high-ignition-quality reference is cetane (n-hexadecane) assigned a cetane number of 100, and the low-ignition-quality reference is alpha-methylnaphthalene assigned a cetane number of 0. A test fuel is matched to a blend of these references to obtain its cetane number. Although a different low-end reference (HMN) is used in some modern standards, the classic textbook pairing remains cetane with alpha-methylnaphthalene. Step-by-Step Solution: Identify high reference: cetane with very short ignition delay (good ignition quality).Identify low reference: alpha-methylnaphthalene with long ignition delay (poor ignition quality).Determine the blend that matches the test fuel ignition delay to read the cetane number. Verification / Alternative check: Diesel fuel test standards and classic engine-fuel texts describe the cetane scale using this pair, explaining the methodology of fuel matching in CFR engines. Why Other Options Are Wrong: Iso-octane and normal heptane are octane-rating references, not cetane. Tetraethyl lead is an antiknock additive for petrol and does not serve as a reference fuel for cetane ratings. Common Pitfalls: Confusing octane and cetane scales or assuming that a modern substitute for the low reference changes the conceptual definition. Final Answer: Cetane and alpha-methylnaphthalene

Q: Four-stroke cycle engines — working strokes per minute For a four-stroke reciprocating engine running at N revolutions per minute, the number of power (working) strokes per minute for one cylinder is:

Introduction / Context: Engine performance calculations often require converting rotational speed to the number of working cycles. In a four-stroke engine, one thermodynamic cycle requires two full crankshaft revolutions, which directly determines the frequency of power strokes per cylinder. Given Data / Assumptions: Four distinct strokes: intake, compression, power, and exhaust. Uniform speed N revolutions per minute. Single cylinder analysis for clarity. Concept / Approach: Each four-stroke cycle spans 720 crank angle degrees, or two complete revolutions. Therefore, each cylinder produces one power stroke every two revolutions. The number of power strokes per minute per cylinder is half the rotational speed. Step-by-Step Solution: Recognize cycle length: 2 revolutions per power event.Relate to speed: power strokes per minute = N / 2 per cylinder.For multi-cylinder engines, total power strokes per minute scale with the number of cylinders. Verification / Alternative check: Timing diagrams in engine textbooks show that only one of the four strokes is the power stroke, confirming the factor of one-half relative to crankshaft speed. Why Other Options Are Wrong: Equal to N, 2N, or 4N would imply a power stroke every revolution or more frequently, which contradicts the four-stroke mechanism. Common Pitfalls: Mixing up two-stroke and four-stroke conventions. A two-stroke engine produces one power stroke per revolution, whereas a four-stroke requires two revolutions. Final Answer: N / 2

Q: Indicated power comparison — multi-cylinder vs single-cylinder engines Evaluate the statement: “The indicated power of a multi-cylinder engine will be the same as that of a single-cylinder engine.” Is this statement true under general conditions?

Introduction / Context: Indicated power is the gross power developed inside the cylinders from pressure-volume work before mechanical losses. It depends on displacement, mean effective pressure, speed, and the number of working units. The architecture of the engine strongly influences the indicated power for a given total displacement and speed. Given Data / Assumptions: Comparing engines not constrained to be identical in cylinder count or configuration. Operating at the same speed and similar mean effective pressure is not guaranteed. Mechanical layout can change gas exchange and combustion quality. Concept / Approach: A multi-cylinder engine can have smoother torque delivery and better breathing, often allowing higher mean effective pressure and speed at similar displacement, which changes indicated power. Even at the same total displacement and speed, distribution of cylinders affects combustion quality and volumetric efficiency, so indicated power need not be identical to that of a single-cylinder engine. Step-by-Step Solution: Recall formula: IP = pmi * L * A * n * N, where pmi is indicated mean effective pressure, and the stroke-bore-geometry factors scale with cylinder count.Recognize that pmi and achievable N are influenced by cylinder sizing and balance.Therefore, the statement claiming equality without conditions is generally false. Verification / Alternative check: Engine families offered in different cylinder counts at the same displacement show different rated outputs because breathing and friction characteristics differ, confirming that indicated power is not inherently the same. Why Other Options Are Wrong: Choosing true would ignore the influence of cylinder count on pmi, speed capability, and combustion stability. Common Pitfalls: Confusing indicated power with total displacement alone; performance arises from multiple interacting parameters including timing, intake, and the number of cylinders. Final Answer: False

Q: Effect of engine speed on indicated power For a given reciprocating engine operating near its efficient range, how does indicated power generally change as the rotational speed increases (other conditions reasonably similar)?

Introduction / Context: Indicated power reflects the rate of doing work inside the cylinder. Speed determines how many cycles occur per unit time, which directly affects indicated power when mean effective pressure is maintained. This is a foundational relation used in engine performance mapping. Given Data / Assumptions: Engine is operated within a range where volumetric efficiency and combustion remain acceptable. Mean effective pressure does not collapse drastically as speed increases. No knock or severe pumping losses limiting output. Concept / Approach: For reciprocating engines, indicated power is proportional to indicated mean effective pressure multiplied by displacement per cycle and cycles per second. If pmi remains approximately steady, increasing speed increases the number of power events per minute, so indicated power rises. At very high speed, pmi may fall due to breathing limits, but the general relationship over a moderate range is increasing indicated power with speed. Step-by-Step Solution: Use proportionality: IP ∝ pmi * displacement per cycle * cycles per minute.As speed N increases, cycles per minute increase in direct proportion.Therefore, provided pmi does not drop excessively, IP increases with N. Verification / Alternative check: Manufacturer performance curves commonly show rising indicated and brake power with speed up to a rated point, after which power plateaus or declines as pmi falls. Why Other Options Are Wrong: Power remaining constant or decreasing would only apply where pmi falls enough to offset the increase in cycles; that is not the general case in the efficient operating band. Common Pitfalls: Extrapolating beyond the efficient range and assuming the same trend continues without accounting for breathing and combustion limits. Final Answer: Increase

Q: Terminology check — what are petrol engines commonly called? Petrol fueled reciprocating engines initiate combustion with an electric spark from a spark plug. These engines are commonly known as:

Introduction / Context: Engine classification is often based on the method of combustion initiation. Petrol engines rely on premixed charge ignition triggered by an electrical spark, whereas diesel engines depend on auto-ignition from high compression temperatures. Given Data / Assumptions: Petrol-type fuel and a throttle-controlled intake. Presence of spark plugs and ignition system. Standard four-stroke or two-stroke SI operation. Concept / Approach: Spark ignition engines initiate combustion using a timed spark to ignite an air-fuel mixture prepared by a carburetor or fuel injection. The idealized thermodynamic model is the Otto cycle with constant-volume heat addition. Compression ignition engines, on the other hand, inject fuel into hot compressed air and rely on auto-ignition, not a spark. Step-by-Step Solution: Identify combustion trigger: electrical spark for petrol engines.Relate to standard terminology: spark ignition (SI).Therefore, petrol engines are commonly called spark ignition engines. Verification / Alternative check: Technical literature abbreviates petrol engines as SI and diesel engines as CI, confirming the accepted naming convention. Why Other Options Are Wrong: Compression ignition refers to diesels. Detonation control and auto-ignition engines are not standard classification terms for petrol engines. Common Pitfalls: Assuming that the presence of occasional knock in petrol engines implies compression ignition; it does not. Normal operation is spark initiated. Final Answer: Spark ignition engines

Q: Interpreting a cetane number of 40 A diesel fuel with cetane number 40 has the same ignition quality as a volumetric blend of which two reference fuels in the specified proportions?

Introduction / Context: The cetane number translates ignition delay into an equivalent mixture of two standard fuels in a calibrated test engine. This enables reproducible comparison between fuels across laboratories and time. Given Data / Assumptions: Cetane number scale with cetane = 100 and alpha-methylnaphthalene = 0 as classic references. Linear interpolation of ignition quality between reference fuels by volume in the standardized method. Concept / Approach: A cetane number of 40 means that the test fuel has the same ignition delay as a blend containing 40% by volume cetane and 60% by volume alpha-methylnaphthalene. The higher the proportion of cetane, the better (shorter delay) the ignition quality. Thus the percentages numerically match the cetane number in the conventional interpretation. Step-by-Step Solution: Identify high and low references: cetane (100), alpha-methylnaphthalene (0).Match ignition delay to an equivalent blend.For CN = 40, the equivalent blend is 40% cetane + 60% alpha-methylnaphthalene. Verification / Alternative check: Standard diesel fuel testing procedures define the reading as the percentage of cetane by volume in the blend that matches ignition delay, confirming this interpretation. Why Other Options Are Wrong: Reversing the percentages would correspond to CN = 60. Petrol and diesel mixtures are unrelated to the cetane reference method. Common Pitfalls: Confusing the octane scale (iso-octane and n-heptane) with the cetane scale; they serve different engine types and properties. Final Answer: 40% cetane and 60% alpha-methylnaphthalene

Question 1

Engine Performance – Definition of Mechanical Efficiency (ηm) In reciprocating internal combustion engines, mechanical efficiency (ηm) is defined to compare the useful shaft output with the power developed inside the cylinder. Which of the following…

Accepted Answer

Introduction / Context: Mechanical efficiency connects what the engine develops in the combustion chamber (indicated power) to what finally appears at the crankshaft (brake power). It highlights mechanical and pumping losses in bearings, piston–ring packs, valve trains, and auxiliaries. Knowing ηm is essential for separating combustion improvements from friction reduction efforts. Given Data / Assumptions: I.P. is the gross power calculated from cylinder pressure–volume data. B.P. is the net power measured at the shaft via a dynamometer. Frictional power F.P. = I.P. − B.P. represents mechanical and pumping losses. Concept / Approach: By definition, mechanical efficiency is the fraction of in-cylinder power transmitted to the shaft. Therefore ηm must relate B.P. to I.P. directly. Because losses are always positive in real engines, ηm is less than 1 and improves when friction or accessory loads are reduced. Step-by-Step Solution: Start from the power balance: I.P. = B.P. + F.P.Rearrange to define mechanical efficiency: ηm = B.P. / I.P.Interpretation: when losses shrink (F.P. smaller), B.P. approaches I.P. and ηm rises toward 1.Relate to friction: F.P. / I.P. = 1 − ηm. Verification / Alternative check: Motoring tests determine F.P. at various speeds. Substituting F.P. into ηm = 1 − (F.P. / I.P.) yields the same ηm as B.P. / I.P., confirming consistency. Why Other Options Are Wrong: Option B inverts the ratio (would exceed 1). Option C equals 1 − ηm (the friction ratio), not ηm itself. Option E is dimensionally incorrect (difference, not ratio). ‘‘None of these’’ is unnecessary because a correct expression exists. Common Pitfalls: Confusing ηm with overall efficiency (B.P. divided by fuel energy) or indicated thermal efficiency (I.P. divided by fuel energy). Also, assuming ηm is constant across speed—friction rises with RPM, so ηm typically drops at high speed. Final Answer: ηm = Brake power (B.P.) / Indicated power (I.P.)

Question 2

Combustion Characteristics – Effect of Higher Compression Ratio in Spark-Ignition Engines Increasing the compression ratio in a petrol (spark-ignition) engine primarily tends to cause which of the following effects on combustion behavior?

Accepted Answer

Introduction / Context: Compression ratio strongly influences temperature and pressure at the end of compression in spark-ignition (SI) engines. This has multiple, sometimes competing, effects on ignition delay, flame speed, and knock propensity. Understanding these effects drives fuel octane selection and limits for efficiency gains. Given Data / Assumptions: Typical SI engine operating near stoichiometric mixture. Higher compression ratio raises end-of-compression temperature and pressure. Fuel octane rating and hot spots in the chamber affect abnormal combustion behavior. Concept / Approach: As compression ratio increases, the unburned end-gas becomes hotter and more reactive. This can shorten the ignition delay and quicken normal flame propagation, but it also moves the end-gas closer to auto-ignition conditions, raising the risk of detonation. Local overheated parts (deposits, plug electrodes) may trigger pre-ignition when the mixture ignites before the spark, a serious fault exacerbated by higher temperatures associated with high compression ratios. Step-by-Step Solution: Relate CR to state: higher CR → higher T and p before ignition.Higher T reduces ignition delay → faster burn (option C).Hotter end-gas increases knock tendency (option B).Hot spots may light the charge early → pre-ignition (option A).Thus, depending on fuel and cooling, any of these effects may appear. Verification / Alternative check: Octane requirement increases with compression ratio. Engines designed for high CR rely on combustion-chamber shaping, charge motion, knock sensors, and cooled EGR to avoid abnormal combustion while reaping efficiency gains. Why Other Options Are Wrong: Picking only one effect ignores that all three are plausible outcomes under different conditions. ‘‘None of these’’ is incorrect because the listed effects are well documented. Common Pitfalls: Confusing pre-ignition with detonation: pre-ignition occurs before the spark; detonation is end-gas auto-ignition after normal flame starts. Both are encouraged by elevated temperatures caused by high CR. Final Answer: any one of these

Question 3

Fuel Injection in Compression-Ignition (Diesel) Engines – Why High Injection Pressure? Why must a diesel injector nozzle deliver fuel at sufficiently high pressure during the end of the compression stroke?

Accepted Answer

Introduction / Context: Compression-ignition engines rely on direct injection of liquid fuel into very hot, high-pressure air. The injector must create the right spray characteristics so that mixing, vaporization, ignition, and combustion proceed quickly and uniformly, preventing smoke and knock while maximizing efficiency. Given Data / Assumptions: Cylinder pressure is very high near top dead center (TDC) at the end of compression. Air temperature is above self-ignition temperature of the fuel. Air motion (swirl/squish) exists to enhance mixing. Concept / Approach: High injection pressure provides the momentum required to push liquid fuel into a high-pressure environment, producing fine atomization (small droplets) and sufficient penetration so that the spray interacts fully with the air core rather than forming wet walls. Properly designed nozzles balance penetration and dispersion to cover the combustion chamber volume while avoiding excessive wall impingement and soot formation. Step-by-Step Solution: Overcome cylinder pressure: injection pressure must exceed in-cylinder pressure to admit fuel (option A).Create small droplets: high velocity at the nozzle promotes atomization and evaporation (option B).Ensure penetration/dispersion: adequate jet momentum and pattern reach the swirling air uniformly (option C).Together these requirements justify high injection pressure → select ‘‘all of the above’’. Verification / Alternative check: Modern common-rail systems use 1000–2500 bar precisely to achieve these outcomes, with multiple injections per cycle for noise and emissions control—evidence of the central role of high injection pressure. Why Other Options Are Wrong: Option E is incorrect: injection does not cool the air; rather, atomization and mixing prepare fuel for auto-ignition in the hot air. Common Pitfalls: Assuming ‘‘more penetration’’ is always better—excessive penetration causes wall wetting and smoke; the goal is adequate, well-distributed penetration and atomization. Final Answer: all of the above

Question 4

Two-Stroke Engines – Number of Crankshaft Revolutions per Working Cycle Evaluate the statement: “In a two-stroke engine, the working cycle is completed in two revolutions of the crankshaft.”

Accepted Answer

Introduction / Context: The term “working cycle” in reciprocating engines refers to the sequence of events comprising intake, compression, combustion/expansion (power), and exhaust. Whether this requires one or two crankshaft revolutions distinguishes two-stroke from four-stroke engines and directly affects specific power and scavenging strategy. Given Data / Assumptions: A conventional crankcase- or externally-scavenged two-stroke engine. Ports and/or valves time gas exchange within one revolution. Combustion occurs once per revolution for each cylinder in a two-stroke engine. Concept / Approach: In two-stroke operation, every revolution produces one power event (one expansion stroke), because intake and exhaust are combined with compression and power within a single crankshaft revolution, using ports and/or a blower to accomplish scavenging. In contrast, a four-stroke engine requires two revolutions for one power stroke. Step-by-Step Solution: Identify two-stroke sequence: compression + power occupy one revolution with scavenging via ports.Hence, there is one power stroke per revolution.Therefore, the working cycle completes in one revolution, not two.Conclude the given statement is false. Verification / Alternative check: Timing diagrams show intake and exhaust port events near BDC within the same revolution; firing frequency equals engine speed (one firing per revolution per cylinder). Why Other Options Are Wrong: Conditions such as opposed-piston geometry, low speed, or supercharging do not change the fundamental one-revolution cycle property of two-stroke engines. Common Pitfalls: Confusing “cycle” with “number of strokes” and assuming two strokes must equal two revolutions; each revolution has two strokes (up and down), so a two-stroke cycle is indeed one crank revolution. Final Answer: Incorrect

Question 5

Diesel Cycle with Fixed Compression Ratio – Effect of Cut-off Ratio on Mean Effective Pressure For a diesel (constant-pressure heat addition) cycle at a fixed compression ratio, how does the indicated mean effective pressure (IMEP) change when the c…

Accepted Answer

Introduction / Context: The cut-off ratio in a diesel cycle is the ratio of cylinder volume at the end of heat addition to that at the start of heat addition. It determines how much heat is added at approximately constant pressure. At a fixed compression ratio, changing cut-off alters net work, thermal efficiency, and mean effective pressure (MEP), which is a convenient load-independent performance metric. Given Data / Assumptions: Ideal air-standard diesel cycle model. Compression ratio r is fixed. Cut-off ratio rc is varied; other losses neglected for the trend analysis. Concept / Approach: IMEP is proportional to net cycle work divided by displacement volume. With smaller rc (shorter heat addition), the amount of heat input per cycle decreases. At constant r, less heat added yields lower expansion work and therefore reduced net work, causing IMEP to fall. Although diesel-cycle thermal efficiency improves when rc is lowered (less late-cycle heat addition at high temperature), the absolute work output diminishes, reducing MEP. Step-by-Step Solution: Relate heat input to rc: smaller rc → less heat added at constant pressure.Compute qualitative effect: less heat added → less expansion work.Net work decreases → IMEP (work per cycle / displacement) decreases.Therefore, IMEP decreases when rc decreases at fixed r. Verification / Alternative check: Air-standard cycle equations show net work proportional to the area of the P–V loop, which shrinks as rc decreases (at fixed r), even though efficiency (work/heat-in) rises. Practical engine maps exhibit similar trade-offs between load (MEP) and combustion phasing/duration. Why Other Options Are Wrong: “Increase” reverses the trend; “remain the same” ignores altered heat input; “first increase then decrease” lacks basis for monotonic rc reduction; “cannot be predicted” is false—trend is well established. Common Pitfalls: Confusing thermal efficiency (which improves with lower rc) with output (which decreases). High efficiency does not necessarily mean high power or MEP. Final Answer: decrease

Question 6

Pressure History in a Petrol (Spark-Ignition) Engine – When Is the Intake Mixture Pressure Lowest? Considering the suction (intake) stroke of a typical carburetted or port-injected petrol engine, at which point is the in-cylinder mixture pressure ge…

Accepted Answer

Introduction / Context: During the intake process in spark-ignition engines, the piston motion, valve timing, and flow losses create a pressure profile below atmospheric. Recognizing when this pressure reaches its minimum aids in understanding volumetric efficiency, throttling effects, and the benefits of variable valve timing. Given Data / Assumptions: Throttle-controlled SI engine operating at part load. Conventional valve timing with intake valve closing slightly after bottom dead center (ABDC). Flow losses in the intake tract and across the valve are present. Concept / Approach: As the piston moves down on the intake stroke, cylinder volume increases, drawing mixture through the intake valve. Due to throttling and valve/port restrictions, cylinder pressure remains below manifold pressure and below ambient. The pressure typically continues to fall and remains at its lowest near the end of the intake stroke when piston speed is still significant and flow inertia sustains a pressure deficit. After the valve closes ABDC, backflow ends and the pressure begins to recover during the early compression stroke. Step-by-Step Solution: Recognize throttling creates sub-ambient manifold pressure.Cylinder pressure tracks manifold pressure but often falls even lower near the end due to flow inertia.Minimum usually occurs close to end of intake (just before IVC).Therefore select “end of suction stroke”. Verification / Alternative check: Indicator diagrams show minimum pressure near late intake. With tuned intakes or VVT, timing shifts the exact minimum, but it remains around the end of the intake event. Why Other Options Are Wrong: At the beginning of intake, pressure is closer to manifold pressure and not yet at minimum. At end of compression, pressure is high. “None of these” and “midway through exhaust” are unrelated to intake minimums. Common Pitfalls: Assuming minimum occurs at the very start; in reality, inertia and valve timing extend the low pressure into late intake. Final Answer: end of suction stroke

Question 7

Events That Reduce Volumetric Efficiency – Vertical Compression-Ignition Engine Which valve-timing event is most likely to reduce the volumetric efficiency of a vertical diesel (compression-ignition) engine?

Accepted Answer

Introduction / Context: Volumetric efficiency (ηv) determines how much fresh air (in a diesel) the cylinder traps per cycle. Valve timing strongly affects ηv by allowing more or less time for induction and by exploiting flow inertia for extra filling after piston reaches BDC. Given Data / Assumptions: Vertical four-stroke CI engine with conventional swirl-inducing ports. Focus on qualitative effect of timing rather than exact crank degrees. Steady operation near rated speed. Concept / Approach: Keeping the inlet valve open slightly after BDC (ABDC) lets the incoming air, which has momentum, continue to flow into the cylinder even as the piston starts rising. This “ram effect” increases trapped mass, improving ηv. Conversely, closing the inlet valve before BDC truncates the induction period, reducing the amount of charge admitted and thus decreasing ηv. Other timing events have smaller or secondary effects on ηv in this context. Step-by-Step Solution: Consider late inlet closing (ABDC): uses flow inertia → higher ηv.Consider early inlet closing (BBDC): curtails induction → lower ηv.Other events (e.g., EVO/EVC timing) influence scavenging overlap but are less directly restrictive to fresh-air admission.Hence, the event that reduces ηv most is inlet valve closing before BDC. Verification / Alternative check: Engine breathing models and experimental tuning show ηv peaking with optimized IVC slightly ABDC; advancing IVC toward BBDC reduces airflow significantly at speed. Why Other Options Are Wrong: ABDC closing usually helps ηv; IVO BTDC assists with overlap/tuning; EVC ATDC affects residuals but not as decisively as premature IVC; EVO BBDC concerns blowdown and does not directly limit induction duration. Common Pitfalls: Assuming any late closing always helps—at very low speed, excessive late closing can cause reversion, but within typical operation, BBDC closing is clearly detrimental. Final Answer: inlet valve closing before bottom dead centre (BBDC)

Question 8

Measurement of Indicated Mean Effective Pressure (IMEP) State whether the following is correct: “The indicated mean effective pressure of an engine is obtained from the indicator diagram drawn with the help of an engine indicator.”

Accepted Answer

Introduction / Context: Indicated mean effective pressure (IMEP) is a load-normalized measure of the work produced inside the cylinder per cycle. It is derived from the pressure–volume history and is central for comparing engines regardless of displacement. Given Data / Assumptions: A mechanical or electronic engine indicator records pressure vs. crank angle. The resulting indicator diagram is converted to a P–V curve over a cycle. Cycle averaging yields indicated work per cycle. Concept / Approach: IMEP is defined as indicated work per cycle divided by displacement volume per cycle. Since indicated work is the area enclosed by the P–V loop, it must be obtained from an indicator diagram (or an equivalent in-cylinder pressure measurement). Traditional mechanical indicators or modern piezoelectric transducers both serve this purpose. Step-by-Step Solution: Acquire in-cylinder pressure trace over a complete cycle.Integrate P with respect to V to get indicated work per cycle.Compute IMEP = Indicated work per cycle / Displacement volume per cycle.Use IMEP for performance comparison independent of size and speed. Verification / Alternative check: Dynamometer-only tests cannot provide IMEP directly; they provide brake power. IMEP requires cylinder pressure data or a validated combustion model tied to it. Why Other Options Are Wrong: Restrictions to two-stroke, supercharged, or full-load operation are unnecessary; IMEP can be obtained for any operating point where a valid indicator diagram is recorded. Common Pitfalls: Confusing IMEP (in-cylinder metric) with BMEP (brake MEP). BMEP is derived from brake torque and displacement, while IMEP requires cylinder pressure. Final Answer: True

Question 9

Brake Thermal Efficiency – Relative Ranking Across Basic Engine Types Arrange the following in decreasing order of typical brake thermal efficiency (highest first): four-stroke compression-ignition (C.I.) engine, four-stroke spark-ignition (S.I.) en…

Accepted Answer

Introduction / Context: Brake thermal efficiency (BTE) reflects how effectively an engine converts fuel energy into shaft power. Different combustion modes and gas exchange strategies lead to characteristic efficiency differences between engine families. Given Data / Assumptions: Steady operation at comparable loads and technology levels. Compression ratios: CI > SI; two-stroke SI suffers from scavenging losses. No hybridization or waste-heat recovery considered. Concept / Approach: Four-stroke CI engines typically achieve the highest BTE due to high compression ratios, lean operation with lower pumping losses, and higher ratio of specific heats during expansion. Four-stroke SI engines rank lower because of throttling (at part load) and knock-limited compression ratios. Two-stroke SI engines generally have the lowest BTE because of short-circuiting/scavenging losses, higher hydrocarbon emissions, and less efficient cylinder filling and combustion control. Step-by-Step Solution: Rank CI vs. SI: CI higher due to higher CR and lean burn advantages.Four-stroke vs. two-stroke SI: four-stroke higher due to better gas exchange and reduced short-circuiting.Combine: Four-stroke CI > Four-stroke SI > Two-stroke SI.Select the option matching this order. Verification / Alternative check: Empirical BTE ranges: modern light-duty SI ~0.30–0.36, CI ~0.38–0.45, small two-stroke SI often <0.30, aligning with the ranking. Why Other Options Are Wrong: Any ordering placing SI ahead of CI or two-stroke SI above four-stroke SI contradicts fundamental thermodynamics and observed scavenging losses. Common Pitfalls: Confusing specific power (which can be high in two-strokes) with efficiency; these are different metrics. Final Answer: four stroke C.I. engine, four stroke S.I. engine, two stroke S.I. engine

Question 10

Detonation Tendency and Self-Ignition Temperature – True or False? Evaluate the statement: “A fuel will detonate less (has lower knock tendency) if it has a higher self-ignition temperature.”

Accepted Answer

Introduction / Context: In spark-ignition engines, detonation (knock) occurs when the unburned end-gas auto-ignites before the flame front arrives. Fuel properties affecting auto-ignition strongly influence knock resistance, which is quantified by octane number. One such property is the self-ignition (auto-ignition) temperature—the temperature at which a mixture spontaneously ignites at a given pressure without an external spark. Given Data / Assumptions: Comparing fuels under the same engine conditions (pressure, mixture strength). Self-ignition temperature is considered alongside other properties (octane sensitivity, evaporation characteristics). Focus on SI knock rather than CI ignition quality. Concept / Approach: A higher self-ignition temperature means the unburned end-gas must reach a higher temperature before auto-ignition can occur. For the same compression ratio and operating point, this delays or prevents end-gas auto-ignition, reducing knock tendency. Thus, fuels with higher auto-ignition temperature, all else equal, are more knock-resistant (higher octane behavior). Note this differs from diesel fuels, where easier auto-ignition (lower ignition delay) is desirable, associated with higher cetane number—not higher self-ignition temperature. Step-by-Step Solution: Define detonation: end-gas auto-ignition producing pressure oscillations.Relate property: higher self-ignition temperature → harder to auto-ignite.Engine implication: for given end-gas conditions, likelihood of knock drops.Conclude statement is true for SI knock tendency. Verification / Alternative check: Octane-boosting components generally raise resistance to auto-ignition. Correlations between octane quality and end-gas reactivity support the role of increased auto-ignition thresholds in reducing knock. Why Other Options Are Wrong: “False” contradicts the thermochemical basis. Conditions like mixture strength and EGR modulate knock but do not reverse the fundamental relation. The claim limited “only in diesel engines” is incorrect because diesel ignition quality follows a different metric (cetane) and aims for easier auto-ignition. Common Pitfalls: Mixing up SI octane with CI cetane: high octane fuels resist auto-ignition (good for SI), while high cetane fuels auto-ignite readily (good for CI). The properties and desired directions are opposite. Final Answer: True

Question 11

Compression-ignition (diesel) engines — strategies to eliminate or reduce knocking In a compression ignition engine, detonation (diesel knock) is mainly caused by a long ignition delay that allows too much fuel to accumulate before auto-ignition. Wh…

Accepted Answer

Introduction / Context: Diesel knock is the characteristic hard combustion noise in compression ignition engines that appears when a large portion of the fuel ignites almost simultaneously after an extended ignition delay. Understanding which parameters reduce ignition delay helps engineers mitigate knock, improve smoothness, and protect the engine. Given Data / Assumptions: Compression ignition engine with conventional fuel injection. Operating point and ambient conditions are fixed for comparison. Knock intensity correlates with ignition delay and the amount of premixed fuel that auto-ignites together. Concept / Approach: Ignition delay is the time between start of injection and the start of combustion. A shorter delay means less fuel accumulates before combustion begins, so the initial heat release is smaller and more progressive. This reduces the rate of pressure rise and therefore the perceived knock. Higher compression ratio and lower fuel self-ignition temperature generally shorten delay, while poor atomization, low charge temperature, or excessive injection advance can lengthen it. Step-by-Step Solution: Identify the cause of knock: large premixed burn due to long ignition delay.Determine remedy: shorten the delay so less fuel auto-ignites at once.Engineering levers include adequate compression ratio, proper injection timing, good spray atomization, and using fuel with favorable cetane number.Therefore, a short delay period directly reduces knocking tendency. Verification / Alternative check: Cetane number is an ignition quality index. A higher cetane number reduces delay. Engines specified for high-cetane fuel exhibit smoother combustion, confirming the principle that shorter delay reduces knock. Why Other Options Are Wrong: Late auto-ignition of the entire injected charge would create violent pressure rise. Low compression ratio increases delay and can worsen knock at start of combustion. A high self-ignition temperature fuel typically lengthens delay and can aggravate knock in a diesel context. Common Pitfalls: Confusing diesel knock with spark-knock in petrol engines. The countermeasures are different because combustion initiation mechanisms differ between compression ignition and spark ignition. Final Answer: Short delay period

Question 12

Nuclear reactor physics — meaning of critical size and critical mass The critical size of a reactor refers to the size at which a self-sustaining chain reaction can be initiated with just enough fissionable material (the critical mass). Is this defi…

Accepted Answer

Introduction / Context: In neutron chain reactions, geometry and material composition determine whether the neutron population grows, decays, or remains steady. The term critical size connects the physical dimensions of a reactor to the concept of critical mass for a given configuration and set of materials. Given Data / Assumptions: Homogeneous or heterogeneous reactor with specified fuel, moderator, and reflector. Steady-state analysis with effective multiplication factor k-effective. Leakage and absorption determine criticality for a given geometry. Concept / Approach: Criticality occurs when k-effective equals 1. At this condition, one fission on average causes exactly one subsequent fission, maintaining a steady neutron population. For a given set of materials, there exists a minimum configuration (critical size) that provides sufficient moderation and reflection to limit leakage so that k-effective reaches unity with a corresponding amount of fissile material known as the critical mass. Step-by-Step Solution: Define criticality: k-effective = 1, neutron production equals losses.Recognize geometric effect: as the system grows, surface-to-volume ratio decreases, reducing leakage.For fixed materials, there is a minimum size at which leakage is low enough for k-effective to reach 1 with a particular fissile content.Hence, the critical size corresponds to the configuration where the chain reaction is just self-sustaining with the critical mass. Verification / Alternative check: Reflectors reduce the required critical size and critical mass by returning escaping neutrons. This practical design strategy confirms the tight link between geometry and the amount of fissile material needed to achieve criticality. Why Other Options Are Wrong: Calling the definition incorrect would ignore the standard usage of critical size and critical mass in reactor physics and shielding design. Common Pitfalls: Assuming critical mass is a single number independent of geometry and reflectors. It varies strongly with configuration and materials. Final Answer: Correct

Question 13

Internal combustion engines — which statements are correct? Consider the following statements about reciprocating engines: (1) Compression ratio for petrol engines typically ranges from 6 to 10. (2) A higher compression ratio in diesel engines resul…

Accepted Answer

Introduction / Context: Basic engine design parameters like compression ratio and thermodynamic ideal cycles strongly influence performance, efficiency, and fuel requirements. This question checks recall of typical values and standard modeling assumptions used in engine theory. Given Data / Assumptions: Conventional spark-ignition petrol engines with modern but naturally aspirated configurations. Conventional compression-ignition diesel engines. Use of ideal cycle models for conceptual understanding. Concept / Approach: Petrol engines avoid excessively high compression ratios to prevent knock with typical fuels, hence the usual range of about 6 to 10 in textbook contexts, though modern engines with knock control can be higher. Diesel engines rely on high compression ratios to achieve auto-ignition, which increases peak pressures. The Otto cycle is the constant-volume heat addition idealization for spark-ignition engines, while the Diesel cycle is the constant-pressure heat addition idealization for compression-ignition engines. Step-by-Step Solution: Evaluate (1): Textbook range 6–10 is historically accurate for SI engines; many practical engines fall near this band.Evaluate (2): Increasing compression ratio increases end-of-compression temperature and pressure; diesels therefore see higher peak pressures.Evaluate (3): SI engines are modeled by the Otto cycle for analysis and comparison.Therefore, all three statements are correct. Verification / Alternative check: Engine design manuals and thermodynamics texts consistently pair petrol engines with the Otto cycle and diesels with the Diesel cycle, and they discuss the respective compression ratio implications. Why Other Options Are Wrong: Any option omitting one of the three correct statements fails to reflect standard engine theory and practice. Common Pitfalls: Confusing ideal cycles with real indicator diagrams, or assuming modern knock sensors invalidate the general compression ratio guidance; the idealized associations remain valid for fundamentals. Final Answer: All of the above

Question 14

Fuel ignition quality — reference fuels for cetane number In the conventional cetane rating scale for diesel fuels, which pair of reference fuels defines the ends of the scale used to match ignition delay in a standardized engine?

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Introduction / Context: Cetane number is the ignition quality index for diesel fuels, analogous to octane number for petrol. It is defined by comparing ignition delay to that of blends of standard reference fuels in a test engine under specified conditions. Given Data / Assumptions: Cetane number scale based on ignition delay time. Reference fuels establish fixed ignition characteristics for calibration. Concept / Approach: Traditionally, the high-ignition-quality reference is cetane (n-hexadecane) assigned a cetane number of 100, and the low-ignition-quality reference is alpha-methylnaphthalene assigned a cetane number of 0. A test fuel is matched to a blend of these references to obtain its cetane number. Although a different low-end reference (HMN) is used in some modern standards, the classic textbook pairing remains cetane with alpha-methylnaphthalene. Step-by-Step Solution: Identify high reference: cetane with very short ignition delay (good ignition quality).Identify low reference: alpha-methylnaphthalene with long ignition delay (poor ignition quality).Determine the blend that matches the test fuel ignition delay to read the cetane number. Verification / Alternative check: Diesel fuel test standards and classic engine-fuel texts describe the cetane scale using this pair, explaining the methodology of fuel matching in CFR engines. Why Other Options Are Wrong: Iso-octane and normal heptane are octane-rating references, not cetane. Tetraethyl lead is an antiknock additive for petrol and does not serve as a reference fuel for cetane ratings. Common Pitfalls: Confusing octane and cetane scales or assuming that a modern substitute for the low reference changes the conceptual definition. Final Answer: Cetane and alpha-methylnaphthalene

Question 15

Four-stroke cycle engines — working strokes per minute For a four-stroke reciprocating engine running at N revolutions per minute, the number of power (working) strokes per minute for one cylinder is:

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Introduction / Context: Engine performance calculations often require converting rotational speed to the number of working cycles. In a four-stroke engine, one thermodynamic cycle requires two full crankshaft revolutions, which directly determines the frequency of power strokes per cylinder. Given Data / Assumptions: Four distinct strokes: intake, compression, power, and exhaust. Uniform speed N revolutions per minute. Single cylinder analysis for clarity. Concept / Approach: Each four-stroke cycle spans 720 crank angle degrees, or two complete revolutions. Therefore, each cylinder produces one power stroke every two revolutions. The number of power strokes per minute per cylinder is half the rotational speed. Step-by-Step Solution: Recognize cycle length: 2 revolutions per power event.Relate to speed: power strokes per minute = N / 2 per cylinder.For multi-cylinder engines, total power strokes per minute scale with the number of cylinders. Verification / Alternative check: Timing diagrams in engine textbooks show that only one of the four strokes is the power stroke, confirming the factor of one-half relative to crankshaft speed. Why Other Options Are Wrong: Equal to N, 2N, or 4N would imply a power stroke every revolution or more frequently, which contradicts the four-stroke mechanism. Common Pitfalls: Mixing up two-stroke and four-stroke conventions. A two-stroke engine produces one power stroke per revolution, whereas a four-stroke requires two revolutions. Final Answer: N / 2

Question 16

Indicated power comparison — multi-cylinder vs single-cylinder engines Evaluate the statement: “The indicated power of a multi-cylinder engine will be the same as that of a single-cylinder engine.” Is this statement true under general conditions?

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Introduction / Context: Indicated power is the gross power developed inside the cylinders from pressure-volume work before mechanical losses. It depends on displacement, mean effective pressure, speed, and the number of working units. The architecture of the engine strongly influences the indicated power for a given total displacement and speed. Given Data / Assumptions: Comparing engines not constrained to be identical in cylinder count or configuration. Operating at the same speed and similar mean effective pressure is not guaranteed. Mechanical layout can change gas exchange and combustion quality. Concept / Approach: A multi-cylinder engine can have smoother torque delivery and better breathing, often allowing higher mean effective pressure and speed at similar displacement, which changes indicated power. Even at the same total displacement and speed, distribution of cylinders affects combustion quality and volumetric efficiency, so indicated power need not be identical to that of a single-cylinder engine. Step-by-Step Solution: Recall formula: IP = pmi * L * A * n * N, where pmi is indicated mean effective pressure, and the stroke-bore-geometry factors scale with cylinder count.Recognize that pmi and achievable N are influenced by cylinder sizing and balance.Therefore, the statement claiming equality without conditions is generally false. Verification / Alternative check: Engine families offered in different cylinder counts at the same displacement show different rated outputs because breathing and friction characteristics differ, confirming that indicated power is not inherently the same. Why Other Options Are Wrong: Choosing true would ignore the influence of cylinder count on pmi, speed capability, and combustion stability. Common Pitfalls: Confusing indicated power with total displacement alone; performance arises from multiple interacting parameters including timing, intake, and the number of cylinders. Final Answer: False

Question 17

Effect of engine speed on indicated power For a given reciprocating engine operating near its efficient range, how does indicated power generally change as the rotational speed increases (other conditions reasonably similar)?

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Introduction / Context: Indicated power reflects the rate of doing work inside the cylinder. Speed determines how many cycles occur per unit time, which directly affects indicated power when mean effective pressure is maintained. This is a foundational relation used in engine performance mapping. Given Data / Assumptions: Engine is operated within a range where volumetric efficiency and combustion remain acceptable. Mean effective pressure does not collapse drastically as speed increases. No knock or severe pumping losses limiting output. Concept / Approach: For reciprocating engines, indicated power is proportional to indicated mean effective pressure multiplied by displacement per cycle and cycles per second. If pmi remains approximately steady, increasing speed increases the number of power events per minute, so indicated power rises. At very high speed, pmi may fall due to breathing limits, but the general relationship over a moderate range is increasing indicated power with speed. Step-by-Step Solution: Use proportionality: IP ∝ pmi * displacement per cycle * cycles per minute.As speed N increases, cycles per minute increase in direct proportion.Therefore, provided pmi does not drop excessively, IP increases with N. Verification / Alternative check: Manufacturer performance curves commonly show rising indicated and brake power with speed up to a rated point, after which power plateaus or declines as pmi falls. Why Other Options Are Wrong: Power remaining constant or decreasing would only apply where pmi falls enough to offset the increase in cycles; that is not the general case in the efficient operating band. Common Pitfalls: Extrapolating beyond the efficient range and assuming the same trend continues without accounting for breathing and combustion limits. Final Answer: Increase

Question 18

Terminology check — what are petrol engines commonly called? Petrol fueled reciprocating engines initiate combustion with an electric spark from a spark plug. These engines are commonly known as:

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Introduction / Context: Engine classification is often based on the method of combustion initiation. Petrol engines rely on premixed charge ignition triggered by an electrical spark, whereas diesel engines depend on auto-ignition from high compression temperatures. Given Data / Assumptions: Petrol-type fuel and a throttle-controlled intake. Presence of spark plugs and ignition system. Standard four-stroke or two-stroke SI operation. Concept / Approach: Spark ignition engines initiate combustion using a timed spark to ignite an air-fuel mixture prepared by a carburetor or fuel injection. The idealized thermodynamic model is the Otto cycle with constant-volume heat addition. Compression ignition engines, on the other hand, inject fuel into hot compressed air and rely on auto-ignition, not a spark. Step-by-Step Solution: Identify combustion trigger: electrical spark for petrol engines.Relate to standard terminology: spark ignition (SI).Therefore, petrol engines are commonly called spark ignition engines. Verification / Alternative check: Technical literature abbreviates petrol engines as SI and diesel engines as CI, confirming the accepted naming convention. Why Other Options Are Wrong: Compression ignition refers to diesels. Detonation control and auto-ignition engines are not standard classification terms for petrol engines. Common Pitfalls: Assuming that the presence of occasional knock in petrol engines implies compression ignition; it does not. Normal operation is spark initiated. Final Answer: Spark ignition engines

Question 19

Interpreting a cetane number of 40 A diesel fuel with cetane number 40 has the same ignition quality as a volumetric blend of which two reference fuels in the specified proportions?

Accepted Answer

Introduction / Context: The cetane number translates ignition delay into an equivalent mixture of two standard fuels in a calibrated test engine. This enables reproducible comparison between fuels across laboratories and time. Given Data / Assumptions: Cetane number scale with cetane = 100 and alpha-methylnaphthalene = 0 as classic references. Linear interpolation of ignition quality between reference fuels by volume in the standardized method. Concept / Approach: A cetane number of 40 means that the test fuel has the same ignition delay as a blend containing 40% by volume cetane and 60% by volume alpha-methylnaphthalene. The higher the proportion of cetane, the better (shorter delay) the ignition quality. Thus the percentages numerically match the cetane number in the conventional interpretation. Step-by-Step Solution: Identify high and low references: cetane (100), alpha-methylnaphthalene (0).Match ignition delay to an equivalent blend.For CN = 40, the equivalent blend is 40% cetane + 60% alpha-methylnaphthalene. Verification / Alternative check: Standard diesel fuel testing procedures define the reading as the percentage of cetane by volume in the blend that matches ignition delay, confirming this interpretation. Why Other Options Are Wrong: Reversing the percentages would correspond to CN = 60. Petrol and diesel mixtures are unrelated to the cetane reference method. Common Pitfalls: Confusing the octane scale (iso-octane and n-heptane) with the cetane scale; they serve different engine types and properties. Final Answer: 40% cetane and 60% alpha-methylnaphthalene

Question 20

Otto cycle idealization — constant-volume heat addition in petrol engines In the idealized analysis of a petrol (spark ignition) engine, the spark initiates combustion that raises pressure and temperature while the piston is momentarily near top dea…

Accepted Answer

Introduction / Context: Thermodynamic cycle models help approximate the complex real processes inside engines. The Otto cycle is the canonical model for spark ignition engines and assumes heat addition at constant volume to simplify analysis and capture first-order behavior. Given Data / Assumptions: Spark ignition near top dead centre. Very short combustion duration compared with piston motion near TDC in the ideal model. Neglect of heat losses and finite-rate effects in the ideal cycle. Concept / Approach: In the Otto cycle, heat addition is modeled as a constant-volume process. Because the piston displacement is minimal during the short ignition and early flame propagation period, the volume is approximated as fixed, so pressure and temperature rise sharply. This distinguishes the Otto cycle from the Diesel cycle, which assumes constant-pressure heat addition during part of combustion in a compression ignition engine. Step-by-Step Solution: Identify the model used for petrol engines: Otto cycle.Recognize the heat-addition idealization: constant volume.Therefore, the statement describing pressure and temperature rise at nearly constant volume is correct within the model. Verification / Alternative check: Real cycles show finite burn duration and some volume change during combustion, but the constant-volume approximation yields reasonable trends for efficiency and pressure ratios, supporting its educational value. Why Other Options Are Wrong: Answering No would conflate the Otto cycle with Diesel or dual cycles, which have different heat-addition assumptions. Common Pitfalls: Assuming that the idealization exactly matches reality. It is a simplifying model used for comparative and preliminary calculations. Final Answer: Yes

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