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This article reports on the potential of negative valve overlap (NVO) for improving the net indicated thermal efficiency (η NIMEP) of gasoline engines during part load. Three fixed fuel flow rates, resulting in indicated mean effective pressures of up to 6 bar, were investigated. At low load, NVO significantly reduces the pumping loses during the gas exchange loop, achieving up to 7% improvement in indicated efficiency compared to the baseline. Similar efficiency improvements are achieved by positive valve overlap (PVO), with the disadvantage of worse combustion stability from a higher residual gas fraction (xr). As the load increases, achieving the wide-open throttle limit, the benefits of NVO for reducing the pumping losses diminish, while the blowdown losses from early exhaust valve opening (EVO) increase.

This work examines the effect of valve timing during cold crank-start and cold fast-idle (1200 rpm, 2 bar NIMEP) on the emissions of hydrocarbons (HC) and particulate mass and number (PM/PN). Four different cam-phaser configurations are studied in detail: 1. Baseline stock valve timing. 2. Late intake opening/closing. 3. Early exhaust opening/closing. 4. Late intake phasing combined with early exhaust phasing. Delaying the intake valve opening improves the mixture formation process and results in more than 25% reduction of the HC and of the PM/PN emissions during cold crank-start. Early exhaust valve phasing results in a deterioration of the HC and PM/PN emissions performance during cold crank-start. Nevertheless, early exhaust valve phasing slightly improves the HC emissions and substantially reduces the particulate emissions at cold fast-idle.

In the thermal expansion valve (TXV) refrigerant system, transient high-pitched whistle around 6.18 kHz is often perceived following air-conditioning (A/C) compressor engagements when driving at higher vehicle speed or during vehicle acceleration, especially when system equipped with the high-efficiency compressor or variable displacement compressor. The objectives of this paper are to conduct the noise source identification, investigate the key factors affecting the whistle excitation, and understand the mechanism of the whistle generation. The mechanism is hypothesized that the whistle is generated from the flow/acoustic excitation of the turbulent flow past the shallow cavity, reinforced by the acoustic/structural coupling between the tube structural and the transverse acoustic modes, and then transmitted to evaporator. To verify the mechanism, the transverse acoustic mode frequency is calculated and it is coincided to the one from measurement.

A deeper understanding of the complex phenomenology associated with the multiphase flow-induced noise and vibration in a dynamic valve is of critical importance to the automotive industry. To this purpose, a two-dimensional axisymmetric numerical model has been developed to simulate the complex processes that are responsible for the noise and vibration in a poppet valve. More specifically, an Eulerian multiphase flow model, a dynamic mesh and a user-defined function are utilized to facilitate the modeling of this complicated two-phase fluid-structure interaction problem. For a two-phase flow through the valve, our simulations showed that the deformation and breakup of gas bubbles in the gap between the poppet and the valve seat generates a vibration that arises primarily from the force imbalance between the spring and the two-phase fluid flow induced forces on the poppet.

The pneumatic air brake system for heavy commercial trucks is composed by a large number of components, aiming its proper work and compliance with rigorous criteria of vehicular safety. One of those components, present along the whole vehicle, is the air brake tube, ducts which feed valves and reservoirs with compressed air, carrying signals for acting or releasing the brake system. In 2011, due to a lack of butadiene in a global scale, the manufacturing of these tubes was compromised; as this is an important raw material present on the polymer used so far, PA12. This article introduces the methodology of selecting, developing and validating in vehicle an alternative polymer for this application. For this purpose, acceptance criteria have been established through global material specifications, as well as bench tests and vehicular validation requirements.

Turbocharged gasoline engines are typically equipped with a compressor anti-surge valve or CBV (compressor by-pass valve). The purpose of this valve is to release pressurized air between the throttle and the compressor outlet during tip-out maneuvers. At normal operating conditions, the CBV is closed. There are two major CBV mounting configurations. One is to mount the CBV on the AIS system. The other is to mount the CBV directly on the compressor housing, which is called an integrated CBV. For an integrated CBV, at normal operating conditions, it is closed and the enclosed passageway between high pressure side and low pressure side forms a “side-branch” in the compressor inlet side (Figure 12). The cavity modes associated with this “side-branch” could be excited by shear layer flow and result in narrow band flow noises.

Rotary valves should pose a credible threat to other mechanical valve systems-such as poppet valves-but they have been unable to infiltrate the automotive market. Using Axiomatic Design we have identified significant design problems with existing rotary valves which have prevented their wide-spread use. In addition, we have proposed an innovative solution which removes some couplings in existing rotary valve systems and could potentially be used in automotive applications, although further work must still be performed.

Intake valve thermal behavior was observed across a wide range of operating conditions while running an engine on both propane and gasoline. Compared to the gaseous fuel, the liquid fuel operation has cooler valve temperatures (∼50-100C difference) and there is significant temperature gradient across the valve surface due to liquid fuel impinging on the front quadrant of the valve. The valve warm-up time is largely determined by the effective thermal inertia of the valve (∼valve body plus 1/3 of stem mass) and the thermal resistance to the seat. The valve is heated up by the combustion chamber; the dominant cooling paths are through the seat contact and the liquid fuel evaporation. Just after starting, very little fuel evaporates from the cold valve until there is a substantial increase in valve temperature in a period of approximately 10-20 seconds.

A new methodology for determining the steady-state flow force on a hydraulic spool valve has been developed. From a solid model of the valve and valve body, a commercially available CFD package automeshes the volume grid and determines the 3D steady-state flow field and forces on the valve within 36 CPU hrs. This numerical approach enables the quick determination of optimal valve design aimed at improved valve controllability and reduced wear in the hydraulic circuit. To demonstrate this methodology, several simulations were performed aimed at investigating the influence of valve design and valve operating conditions on the steady-state flow force experienced by the valve. The numerical simulations showed that a tapered spool geometry can introduce significant variations in the axial and radial forces (30%).

The presence of liquid fuel inside the engine cylinder is believed to be a strong contributor to the high levels of hydrocarbon emissions from spark ignition (SI) engines during the warm-up period. Quantifying and determining the fate of the liquid fuel that enters the cylinder is the first step in understanding the process of emissions formation. This work uses planar laser induced fluorescence (PLIF) to visualize the liquid fuel present in the cylinder. The fluorescing compounds in indolene, and mixtures of iso-octane with dopants of different boiling points (acetone and 3-pentanone) were used to trace the behavior of different volatility components. Images were taken of three different planes through the engine intersecting the intake valve region. A closed valve fuel injection strategy was used, as this is the strategy most commonly used in practice. Background subtraction and masking were both performed to reduce the effect of any spurious fluorescence.

As part of a general EGR system model, an adiabatic thermodynamic vacuum EGR valve actuator model was developed and validated. The long term goal of the work is improved system operation by correctly specifying and allocating EGR system component requirements.

A 1.9L four cylinder engine was evaluated for leakage of cylinder charge through the exhaust valve seats. Fast FID HC analyzer traces reveal leakage. Static leakdown tests do not correlate with the Fast FID measurement, unlike previously published reports for a different engine. The causes of exhaust valve seat leakage are likely to be Flakes of cylinder deposits lodging in the valve seat Valve seat distortion due to the thermal and pressure loading of the cylinder head structure Because deposit related effects are very history dependent, it is very difficult to obtain quantitative results. Some experimental observations: Static pressure leakage measurements show variation of leakage area with cylinder pressure, caused by flexing of the valve head. Dynamic leakage results are history dependent. Leakage is reduced after running at high speed/load, and gradually build up during extended light load low speed operation.

The occurrence of liquid fuel in the cylinder of automotive internal combustion engines is believed to be an important source of exhaust hydrocarbon (HC) emissions, especially during the warm-up process following an engine start up. In this study a Phase Doppler Particle Analyzer (PDPA) has been used in a transparent flow visualization combustion engine in order to investigate the phenomena which govern the transport of liquid fuel into the cylinder during a simulated engine start up process. Using indolene fuel, the engine was started up from room temperature and run for 90 sec on each start up simulation. The size and velocity of the liquid fuel droplets entering the cylinder were measured as a function of time and crank angle position during these start up processes. The square-piston transparent engine used gave full optical access to the cylinder head region, so that these droplet characteristics could be measured in the immediate vicinity of the intake valve.

The 1997 Ford Explorer introduces a new two valve single overhead cam (SOHC) version of the 4.0L V6 engine. Maximum power output is increased to 153 KW net (205 HP) at 5000 rpm and 340 N-M of torque (250 lb-ft) at 3000 rpm, which represents a 28% increase in power and an 11% increase in torque over the existing 4.0L overhead valve (OHV) design. The new design's performance features are single overhead camshafts driven by a patented “Offset Y-drive” dual stage chain system, a plastic variable induction system, and aluminum cylinder heads. For quieter and smoother operation, a main bearing ladder frame and a unique second-order balance shaft (4x4 only) are added.

During the fuel injection process, the flow is mainly metered by the smallest flow area inside the injector. There are two possible locations for the smallest flow areas: at the nozzle and at the valve. In the initial and final stages as the needle is only slightly lifted, the valve area is the metering area. In the fully open stage, the nozzle area is usually smaller than the valve area. However, if the valve area is not much larger than the nozzle, some of the flow may be metered at the valve. This is generally true for injectors with larger nozzles. Objective of this work is to find out how the needle lift affects the static flow, so as to ensure proper control of the needle lift and thus the injector metering process. Three injectors with three different nozzle sizes were studied through CFD analysis. The computational domains cover from the valve to the injector exit for needle lifts of 30-80 μm.

The search for fuel efficient engines that also offer good performance and fuel economy at moderate cost prompted the development of the Split Port Induction (SPI) concept at Ford Motor Company. Ford has upgraded two families of 2-valve engines, the 2.0L CVH 14 and the 3.8L and 4.2L Essex V6's, with the Split Port Induction concept. SPI offers an improved WOT torque curve, better part load dilution tolerance for fuel economy and superior idle combustion stability. This is accomplished by dividing the intake port into two passages and inserting an intake manifold runner control (IMRC) valve into the secondary passage. The opening of this valve determines the level of in-cylinder charge turbulence and volumetric efficiency according to engine operating conditions. The development of the concept and the improvements resulting from its application to these engines will be described and discussed.

A Lagrangian random vortex-boundary element method has been developed for the simulation of unsteady incompressible flow inside three-dimensional domains with time-dependent boundaries, similar to IC engines. The solution method is entirely grid-free in the fluid domain and eliminates the difficult task of volumetric meshing of the complex engine geometry. Furthermore, due to the Lagrangian evaluation of the convective processes, numerical viscosity is virtually removed; thus permitting the direct simulation of flow at high Reynolds numbers. In this paper, a brief description of the numerical methodology is given, followed by an example of induction flow in an off-centered port-cylinder assembly with a harmonically driven piston and a valve seat situated directly below the port. The predicted flow is shown to resemble the flow visualization results of a laboratory experiment, despite the crude approximation used to represent the geometry.

The disk-type gasoline injector uses a flat disk with a seal ring to control the valve opening and the flow rate. Though the disk-type injectors provide several advantages over the pintle-type injectors, some disk injector drips and produces undesired large droplets after several minutes of operation. High-speed photography shows that the injector dripping problem could be a result of slow droplets coming out of the injector at the end of the injection cycle. Namely, a second slow spray is generated. Purpose of this work is to employ the Computational Fluid Dynamics (CFD) techniques to identify the causes of the slow droplets and to improve the injector design. The CFD analysis thus focuses only on the closing stage of the injection cycle. The computational domain in the valve decreases with the time; the transient grid sizes and locations are determined by a constant valve closing velocity.

In order to understand how unburned hydrocarbons emerge from SI engines and, in particular, how non-fuel hydrocarbons are formed and oxidized, a new gas sampling technique has been developed. A sampling unit, based on a combination of techniques used in the Fast Flame Ionization Detector (FFID) and wall-mounted sampling valves, was designed and built to capture a sample of exhaust gas during a specific period of the exhaust process and from a specific location within the exhaust port. The sampling unit consists of a transfer tube with one end in the exhaust port and the other connected to a three-way valve that leads, on one side, to a FFID and, on the other, to a vacuum chamber with a high-speed solenoid valve. Exhaust gas, drawn by the pressure drop into the vacuum chamber, impinges on the face of the solenoid valve and flows radially outward.

The fuel injection process in the port of a firing 4-valve SI engine at part load and 25°C head temperature was observed by a high speed video camera. Fuel was injected when the valve was closed. The reverse blow-down flow when the intake valve opens has been identified as an important factor in the mixture preparation process because it not only alters the thermal environment of the intake port, but also strip-atomizes the liquid film at the vicinity of the intake valve and carries the droplets away from the engine. In a series of “fuel-on” experiments, the fuel injected in the current cycle was observed to influence the fuel delivery to the engine in the subsequent cycles.