ACTIVE DRAG-REDUCTION SYSTEM AND A METHOD OF REDUCING DRAG EXPERIENCED BY A VEHICLE

Abstract

An active drag-reduction system has first 22 and second 24 fluid outlets located on a vehicle 10 adjacent to a low pressure (drag) region 12, wherein fluid ejected from the second fluid outlet 24 is at a higher pressure/ejection velocity than from the first fluid outlet 22. Turbulent and/or low pressure regions adjacent to vehicles are not uniform, but rather have a varying intensity. For instance, the centre of a region may have a lower pressure and/or more turbulent nature than the periphery of the region. The system injects relatively higher pressure air or relatively higher speed air into the relatively lower pressure/more turbulent part of the low pressure/turbulent region, and relatively lower pressure air or relatively lower speed air into the relatively higher pressure/less turbulent part of the low pressure/turbulent region, compared to each other.

Description

RELATED APPLICATIONS

This application is a continuation of U.S. application Ser. No. 17/147,885, filed Jan. 13, 2021, which is a continuation-in-part of U.S. application Ser. No. 16/293,619, filed Mar. 5, 2019, which claims priority under 35 U.S.C. § 120 to, and is a continuation of, International Application PCT/GB2016/052729, filed Sep. 5, 2016 and designating the US. These applications are incorporated by reference herein in their entireties.

BACKGROUND

Field

The present invention relates generally to an active drag-reduction system for vehicles and a method of reducing drag experienced by vehicles moving at speed and finds particular, although not exclusive, utility when applied to aeroplanes, aerofoils (including those used in wind turbines), automobiles, cars, lorries, trains and motorbikes.

Drag (also referred to as fluid resistance) experienced by moving vehicles of various different types comprises three main components: skin friction encountered in laminar flow, which is approximately proportional to the velocity of the vehicle in question; form drag encountered in turbulent flow, which is approximately proportional to the square of the velocity of the vehicle; and vortex drag, for example wingtip, trailing or lift-induced vortices, which are circular patterns of rotating air left behind a wing as it generates lift, in particular at the wing tips, but also at any point on the wing where the lift varies span-wise, at the edge of flap devices, or at other abrupt changes in wing planform.

SUMMARY

It is desirable to minimise all forms of trailing vortices from a moving vehicle, whether they are from turbulent form drag of a vehicle or from vortex drag, for instance by ensuring that the maximum proportion of the drag is due to skin friction. Turbulent flow around a vehicle occurs during flow separation, when a low pressure and/or turbulent vortex region is formed (for instance, behind the vehicle), characteristic of a high Reynolds number in which turbulent flow dominates over laminar flow. In some vehicles multiple smaller vortices may form around the vehicle; in other vehicles, relatively large vortices may be formed. Elimination of these through shaping of bodywork of vehicles is common practice to increase efficiency of the vehicle.

It is also desirable to minimise vortex drag in particular, as wingtip vortices on aircraft can persist for relatively long times (of the order of several minutes after the passage of an aircraft) which can cause danger to other aircraft, in particular around airfields where time must be left between subsequent take-offs and/or landings on a given runway for such vortices to dissipate.

According to a first aspect of the present invention, there is provided an active drag-reduction system for a vehicle in which at least one turbulent and/or low-pressure region is formed adjacent to the vehicle when moving at a speed above a predetermined threshold speed, the active drag-reduction system configured to reduce the at least one turbulent and/or low-pressure region when activated, the active drag-reduction system comprising: at least one convergent propelling nozzle located adjacent to a boundary of the at least one region; at least one divergent propelling nozzle located adjacent to the at least one region and spaced from the boundary of the at least one region, the at least one divergent propelling nozzle arranged to eject fluid substantially toward an interior of the at least one region; and a device for providing gas to each of the at least one convergent and divergent propelling nozzles for expulsion into the at least one region.

According to a second aspect of the present invention, there is provided an active drag-reduction system for a vehicle in which at least one turbulent and/or low-pressure region is formed adjacent to the vehicle when moving at a speed above a predetermined threshold speed, the active drag-reduction system configured to reduce the at least one turbulent and/or low-pressure region when activated, the active drag-reduction system comprising: at least one propelling nozzle located adjacent to the at least one region and arranged to eject fluid substantially toward an interior of the at least one region; and a device for providing gas to the at least one nozzle for expulsion into the at least one region; wherein the at least one propelling nozzle comprises a tip ring supersonic nozzle and/or elliptic sharp tipped shallow lobed nozzle.

Turbulent and/or low pressure regions adjacent to vehicles are not uniform, but rather have a varying intensity. For instance, the centre of a region may have a lower pressure and/or more turbulent nature than the periphery of the region. In this way, therefore, the present invention allows the system of the present invention to inject relatively higher pressure air (or relatively higher speed air) into the relatively lower pressure/more turbulent part of the low pressure/turbulent region, and relatively lower pressure air (or relatively lower speed air) into the relatively higher pressure/less turbulent part of the low pressure/turbulent region, compared to each other.

The at least one first and second fluid outlets may be configured to encourage laminar flow adjacent to a surface of the vehicle on which they are located.

In particular, the fluid ejected into the at least one region may act to fill the low-pressure and/or turbulent region, and may also act to draw adjacent laminar flow toward it (e.g. in accordance to Bernoulli's principle).

The at least one first fluid outlet may be located on the vehicle adjacent to a perimeter of the at least one region.

The at least one first fluid outlet may be arranged to eject fluid substantially parallel to a periphery of (e.g. tangentially to) the at least one region. That is, the at least one fluid outlet may be arranged such that, prior to activation of the system, fluid ejected therefrom would be directed substantially parallel to the periphery of the at least one region; however, subsequent to activation of the system, the size and shape of the region may be modified such that fluid ejected therefrom may be directed in a direction substantially non-parallel to the periphery of the at least one region.

The at least one second fluid outlet may be arranged to eject fluid substantially toward an interior of the at least one region. For instance, the at least one second fluid outlet may be located on an aircraft wing to direct relatively high pressure or fast air into the centre of a wing-tip vortex, and/or the at least one first fluid outlet may be located on an aircraft wing to direct relatively low pressure or slow air along the bounding surface of the wing-tip vortex.

Alternatively of additionally, a plurality of second fluid outlets may be located along a trailing edge of an aerofoil. Optionally, a plurality of first fluid outlets may be arranged substantially above and/or below the plurality of second fluid outlets.

The at least one first fluid outlet may comprise only one, two, three, four, five or more first fluid outlets. For instance, the first fluid outlets may be arranged in a row along an edge of the vehicle. Fluid ejected therefrom may be ejected at a speed sufficient to encourage the Coanda effect in fluid passing over that edge; that is, laminar flow may be encouraged around the edge.

The at least one second fluid outlet may comprise only one, two, three, four, five or more first fluid outlets. For instance, the second fluid outlets may be arranged in a row and/or an array spaced from the edge of the vehicle.

The system may further comprise at least one third fluid outlet located on the vehicle adjacent to the at least one region and spaced from the at least one first fluid outlet and the at least one second fluid outlet; and the fluid supply system may be configured to: provide fluid at a third pressure and/or third ejection velocity to the at least one third fluid outlet, wherein the third pressure and/or third ejection velocity is greater than the first pressure and/or first ejection velocity, and less than the second pressure and/or first ejection velocity, respectively. The system may further comprise at least one fourth, fifth, etc. fluid outlet similar, mutatis mutandis, to the at least one third fluid outlet.

The first pressure and/or first ejection velocity may be between 4% and 35% of the second pressure and/or second ejection velocity, in particular between 5% and 20%, more particularly between 6% and 10%, for instance approximately 6%, 7% or 8%.

Similarly, the third pressure and/or third ejection velocity may be between 8% and 40% of the second pressure and/or second ejection velocity, in particular between 10% and 35%, more particularly between 12% and 20%, for instance approximately 12%, 15% or 18%.

In one arrangement, a first row of first fluid outlets is provided immediately below a spoiler of a car, a second row of second fluid outlets is provided immediately above a rear bumper/fender of a car, and (optionally) a third row of third fluid outlets is provided between the first row and the second row (for instance approximately half-way between).

The system may be configured to supply relatively high temperature fluid to the at least one first and/or second fluid outlets. The relatively high temperature fluid may have a temperature of between 70 and 130 degrees centigrade, in particular between 90 and 120 degrees centigrade, more particularly approximately 110 degrees centigrade.

The system may be configured to supply relatively low temperature gas to the at least one second and/or first fluid outlets. The relatively low temperature gas may have a temperature of between −50 and 10 degrees centigrade, in particular between −40 and −10 degrees centigrade, more particularly approximately −30 degrees centigrade.

The relatively high and the relatively low temperatures referred to may be relative to one another, and/or relative to ambient temperature and/or approximately 20 to 30 degrees centigrade. That is, the system may be configured to supply fluid to the first fluid outlet(s) at a temperature substantially higher or lower than to the second fluid outlet(s).

The system may heat and/or cool gas to provide the relatively high and relatively low temperature gas by any conventional means, for instance, electrical heating, via heat form a coolant system of an engine within the vehicle, from a heat exchanger with for instance exhaust gases, from the heat of compression of gas, from cooling due to expansion of the gas, from a heat exchanger with ambient air, from a refrigeration system, from a liquid nitrogen storage system, or due to passage down a corrugated pipe/tube or due to passage down a pipe/tube having an uneven and/or non-smooth interior.

The system may comprise a vortex tube configured to split gas into a relatively high temperature stream and a relatively low temperature stream, and may be configured to convey the high temperature stream to the at least one first and/or second fluid outlets and the low temperature stream to the at least one second and/or first fluid outlets, respectively.

The vortex tube may be a Ranque-Hilsch vortex tube, for instance of any known configuration. In particular, the vortex tube may comprise a swirl chamber and/or a conical nozzle, as is well known in the art.

The system may comprise a pump (e.g. an air pump as described below) a compressor (e.g. an air compressor as described below) or any other system for providing fluid, gas and/or air to the region via the outlets, preferably in a compressed form compared to ambient; this will be referred to herein as ‘compressed air’, but is intended to cover all stated possibilities unless otherwise stated. A pump may provide fluid directly to an outlet, or may provide fluid to a vortex tube that may then provide a relatively hot gas stream to one outlet and a relative cold gas stream to another outlet. The pump may be in the form of a compressed air pump, or may be a compressor located at an engine inlet (for instance as is present in a turbo charger), where compressed air may be bled off before introduction into the engine.

The exhaust of an engine (e.g. an internal combustion engine) may provide gas (e.g. exhaust gas) directly to a nozzle, or may provide gas to a vortex tube that may then provide a relatively hot gas stream to one nozzle and a relatively cold gas stream to another nozzle.

In some embodiments, gas from a pump may be combined with bled-off and/or exhaust gas before being provided to a nozzle and/or a vortex tube in the manner described above. In alternative embodiments, relatively hot or cold gas streams from a vortex tube may be combined with bled-off and/or exhaust gas before being provided to a nozzle. In this way, noise due to the turbulent motion of the bled-off and/or exhaust gas can be reduced, thereby reducing overall engine noise. In particular, reducing the temperature of the exhaust gas reduces the sound energy carried with the exhaust gas. Combining the gas from the pump and/or vortex tube may be by mixing, for instance by providing the exhaust gas into gas flow (or vice versa) via a coaxial pipe arrangement and/or via a mixer nozzle, for instance a spray nozzle, a duplex nozzle and/or a sewer nozzle. The mixer nozzle may have a primary outlet that provides gas flow therethrough in a substantially continuous direction, and at least one secondary outlets that provide gas flow therethrough in a substantially deflected direction. The deflected direction may be between 10 and 170 degrees, for instance, approximately 15 degrees, 30 degrees, 70 degrees, 90 degrees, 110 degrees or 130 degrees.

In one embodiment, gas from the pump is split into a first stream that is directed to the vortex tube and a second stream that is delivered for combination with exhaust gas.

The gas after combination may have a relatively high or a relatively low temperature, and may be directed to an appropriate portion of the region as discussed above. Preferably, the combined gas has a relatively low temperature and is directed to a nozzle directed towards an interior portion of the region, spaced from a boundary of the region.

In some arrangements, the system may be reversed such that relatively high temperature air is expelled into a high pressure region in front of the vehicle, which may be present due to ram forces. The injected relatively high temperature air may warm the high pressure region, encouraging it to expand and dissipate; in any event, however, the higher temperature air is less dense than the ambient air. The less dense air replaces the ambient air in the high pressure region, and due to the lower density drag is reduced. In particular, in some specific arrangements, outlets may be directed toward relatively high pressure regions adjacent to the vehicle. In effect, this system may act as a virtual and/or invisible air splitter, for example serving to increase the amount of downforce at the front of a car on to which it is applied. An incoming airstream may be brought to stagnation by the expelled air, causing an area of high pressure. Below, air is redirected away from the stagnation zone and is accelerated, causing a pressure to drop, thereby creating downforce.

A further optional alternative would be to configure the system to blow relatively cool air (compared to ambient) over the surface of an aerofoil, for example during take-off of an aircraft. The cooler air is denser than ambient air, and therefore the density of air is increased locally around the wing. Lift generated by an aerofoil is proportional to the density of the air in which it acts; therefore, in this manner, more lift can be generated. This may be of particular use in hot environments where take-off from a ground-level runway can be severely impacted by high temperatures. Such relatively cool air may be blown over the surface of the aerofoil by a plurality of holes in the surface of the aerofoil, in particular on the high pressure side of the aerofoil (e.g. beneath an aircraft wing, or above an aerofoil wing on a car). Similarly, relative warm air (compared to ambient and/or the relatively cool air) may be blown over the surface of the aerofoil, in particular on the low pressure side of the aerofoil (e.g. beneath an aircraft wing, or above an aerofoil wing on a car). These modifications may in particular be used in relation to wind turbine blades.

The fluid outlets may comprise at least one propelling nozzle. The propelling nozzle may be located at an exhaust and/or air outlet. The gas referred to may be air, atmospheric air, engine exhaust, other gases, or a combination thereof. The region may be behind the vehicle, located on a wing and/or aerofoil of a vehicle, behind the cabin of a lorry, or in any other low pressure region adjacent to the vehicle.

The propelling nozzle may comprise a convergent and/or a divergent propelling nozzle. The propelling nozzle may have a pressure ratio defined as the outlet pressure divided by the inlet pressure. In the case of a convergent nozzle, if the nozzle pressure ratio is above a critical value (typically between approximately 1.6:1 to 2:1, e.g. about 1.8:1), the nozzle will choke, resulting in some expansion to ambient pressure taking place downstream of the nozzle throat (i.e. the portion of the nozzle having the smallest cross-sectional flow area); that is, in the jet wake. In this way, the imbalance between the throat static pressure and ambient pressure generates some (pressure) thrust.

The propelling nozzle may be, for example, a convergent-divergent propelling nozzle, which may be a form of divergent propelling nozzle. In a convergent-divergent nozzle, expansion occurring downstream of the convergent nozzle section acts against the inside of the divergent nozzle portion.

The propelling nozzle may comprise an ejector nozzle. The propelling nozzle may comprise a divergent propelling nozzle. Alternatively or additionally, the propelling nozzle may comprise a convergent propelling nozzle, for instance such that the convergent propelling nozzle is configured to produce a relatively high velocity jet, for instance when compared to the velocity of gas introduced to the convergent propelling nozzle and/or the velocity of gas expelled from the divergent propelling nozzle.

The at least one first fluid outlet may be located adjacent to a boundary of the region. That is, the at least one first fluid outlet may be located to direct a jet of fluid into a boundary/boundary-layer of the region. The region may be a turbulent boundary layer, and the boundary of the region may be the extent of the boundary layer. The at least one first fluid outlet may be located such that the extent of the boundary layer is reduced.

A high velocity jet may eliminate the region boundary/vortex boundary/eddy line by inducing the gas therein to equalise speed with gas outside the region.

The divergent nozzle may be configured to produce a relatively high pressure jet, for instance when compared to the pressure of gas introduced to the nozzle and/or the pressure of gas expelled from the convergent propelling nozzle.

The at least one second fluid outlet may be spaced from a boundary of the region. That is, the at least one second fluid outlet may be located to direct a jet of gas into the region, for instance into a central part of the region, a part of the region spaced from a boundary/boundary-layer of the region. Where ‘spaced’ with reference to the location of the divergent nozzle may be viewed as a comparative term to ‘adjacent to’ with reference to the location of the convergent nozzle.

A high pressure jet may act to remove the low pressure region by expanding into said region.

The propelling nozzle may accelerate the available gas to subsonic, sonic, or supersonic velocities. The internal shape may be convergent or convergent-divergent. The propelling nozzle may have a fixed geometry, or they may have variable (i.e. controllable) geometry to give different exit areas to control the characteristics of the propelling jet. The propelling nozzle may be an ejector nozzle; however, other nozzle configurations are contemplated.

The propelling nozzle may be a supersonic ejector, for instance a conical nozzle; however, a tip ring nozzle, or an elliptic sharp tipped shallow (ESTS) lobed nozzle, as described in “Novel supersonic nozzles for mixing enhancement in supersonic ejectors”, Srisha M. V. Raoa & G. Jagadeesh, Applied Thermal Engineering, Volume 71, Issue 1, 5 Oct. 2014, Pages 62-71, the contents of which is incorporated by reference herein in its entirety. Such preferred arrangements provide enhance mixing over that evident from a conical nozzle, for example a 30% increase in entrainment of secondary flow, and also provide a reduction in compression ratio of between 15% and 50%. In a conventional cone-shaped nozzle, the jet is ejected with massive momentum, carrying huge energy and creating noise. However, in the preferred nozzle configurations, the jet is spread and assimilated into the cold atmosphere more quickly, making the jet quieter and improving the ‘push’ provided by the propelling nozzle. Potentially, this could lead to a reduction in sound of between 25% and 35%.

The tip ring nozzle may comprise a divergent nozzle having a circular ring protruding at the exit of a conical nozzle. In particular, the tip ring nozzle may comprise a convergent-divergent nozzle, at the internal periphery of the outlet of the divergent nozzle section there may be provided an annular protrusion extending into the flow, the protrusion having a form that may be substantially ring-like (e.g. donut-shape or toroidal), and extending into the flow from the interior of the divergent nozzle section by approximately 5% of the radius of the divergent nozzle section outlet (e.g. between 2% and 10%, in particular between 4% and 8%, for instance 5 to 7%.

The elliptic sharp tipped shallow (ESTS) lobed nozzle may have elliptic lobes with relatively sharp tips (e.g. forming a cusp between the lobes), the tips protruding only a relatively short distance into the flow). In particular, they may project between approximately 5% and 20% of the radius of the nozzle outlet, more particularly between approximately 7% and 15%, for example 10%. The ESTS lobed nozzle may comprise a conventional lobed nozzle modified to have lobes with an elliptical cross-section projecting radially outward, and with cusps defining the join between adjacent elliptical regions, the cusps projecting inwardly from the interior wall of the divergent nozzle section by between approximately 5% and 20% the radius. In some arrangements, substantially the entire divergent nozzle section has such a cross-sectional form. In preferred embodiments, the nozzle may comprise four lobes; however, three, five, six or more lobes are also envisaged. The ESTS lobed nozzle may comprise a convergent-divergent nozzle.

The propelling nozzle may comprise aluminium alloy.

According to a third aspect of the invention, there is provided a method of reducing vehicular drag, the method comprising the steps of: providing a system according to the first or second aspect; and expelling gas from the at least one nozzle into an interior of the at least one region.

Alternators in motor vehicles are typically driven by the crankshaft, which converts the reciprocal motion of a piston into circular movement. Some early model vehicles used a separate drive belt from the crankshaft pulley to the alternator pulley, but most cars today have a serpentine belt, or one belt that drives all components that rely on crankshaft power. However, as more power is drawn from the crankshaft to operate such ‘accessory components’, the net or effective power output of the engine decreases for producing useful work such as for locomotion.

According to a fourth aspect of the present invention, there is provided a vehicle configured such that, when moving at a speed above a predetermined threshold speed, at least one turbulent and/or low-pressure region is formed adjacent to the vehicle, the vehicle comprising an engine system comprising: an internal combustion engine having an intake and an exhaust; a turbine connected to the exhaust such that the turbine rotates in response to receiving exhaust gases from the engine; an alternator connected to the turbine such that the alternator generates electrical power in response to rotation of the turbine; and an exhaust outlet connected to the turbine, for removing exhaust gases that have been used to rotate the turbine, the exhaust outlet comprising a propelling nozzle located on a rear of the vehicle such that the exhaust gases are expelled substantially toward an interior of a turbulent and/or low-pressure region behind the vehicle; wherein the exhaust provides gas directly to the nozzle.

In this way, the engine is not required to drive the alternator directly, for instance with a crankshaft, thus the alternator does not draw power from the engine, which would otherwise reduce the power available from the engine for locomotion. In contrast, according to the present invention, the alternator is driven by the exhaust gases leaving the engine, which allows all power generated by the engine (and fed into the crankshaft) to be used for primary purposes, such as locomotion. Hence, for a given desired power output of an engine, a smaller (therefore lighter), and potentially more efficient, engine may be used, as the net power output will be higher than that of a conventional engine in which the alternator is connected to the crankshaft.

Exhaust gases from an internal combustion engine are typically at higher temperature and/or pressure than ambient. The turbine may be configured to operate as a turboexpander, such that the relatively high-pressure exhaust gas is expanded to produce work (i.e. to rotate the turbine). In doing so, thermal energy from the exhaust gas is extracted and converted to rotational energy of the turbine; that is, as the exhaust gas expands through the turboexpander, the temperature of the exhaust gas drops as heat energy is converted to rotational kinetic energy of the turbine (e.g. rotation of an impeller or rotor).

The turbine may be any form of known turbine. The turbine may comprise an impulse type turbine, for instance a Pelton wheel turbine, for extracting energy from the impulse of the moving fluid. Alternatively or additionally, the turbine may be a reaction type turbine. The turbine may have a multi-blade construction. For instance, the turbine may comprise a double-blade turbine. The turbine may have only one turbine stage, or a plurality of turbine stages (e.g. two stages). Each turbine stage may be of a similar type, or may differ from some or all other stages. The turbine or impeller may be, for instance, an aluminium alloy, that may be selected to resist the high temperature and pressures encountered within the fluid flow; however, other constructions are also contemplated, such as ceramics and/or other metals. The turbine may comprise bearings (for instance low-friction bearings, such as polymer bearings) upon which an impeller or rotor rotates.

In addition, exhaust gases from an internal combustion engine typically have a relatively high velocity; that is exhaust gases from the internal combustion engine (expelled from the cylinder) are not usually vented to ambient immediately, but are rather conveyed along an exhaust pipe. The pressure of exhaust gases from the cylinder pushes exhaust gasses within the pipe, such that the exhaust gases obtain a velocity through the pipe. In the present invention, the turbine may be arranged to receive such exhaust gases having a velocity, and may be configured to extract kinetic energy due to their velocity. In this way, a ram pressure due to a velocity of the exhaust gases relative to the turbine may be present on the turbine, and the turbine may use this ram pressure to extract kinetic energy from the flowing exhaust gases, and convert it into rotational kinetic energy of the turbine.

A reduction in pressure and/or velocity of the exhaust gases across the turbine may act to reduce the amount of sound energy in the exhaust gases. In particular, the turbine may be configured to convert some sound energy in the exhaust gases into kinetic energy. The turbine may be configured or further configured to dampen incoherent vibrations within the exhaust gases, thereby reducing volume of any sound from the exhaust gases.

The turbine may be configured to rotate at a predetermined RPM in response to receiving exhaust gas from the engine, for instance above approximately 2000 rpm, between approximately 2500 and 8000, in particular between approximately 3000 and 6000 rpm, more particularly between approximately 3500 and 5000 rpm (e.g. approximately 4000 or 4500 rpm). In this way, no gearbox is required between the turbine and the alternator to generate desired electrical power at the alternator. Further, as the alternator is connected to the turbine rather than a crankshaft of the engine, no gearing is required between the crankshaft and the alternator, thus allowing smaller and lighter overall engine size.

Configuring the turbine to rotate at a predetermined RPM may include using a wastegate on the exhaust, to limit the upper rotational speed of the turbine by removing a portion of the exhaust gases from the exhaust before interaction with the turbine, and/or selecting a suitable turbine blade configuration (including angle of attack), using conventional methods.

The alternator may be connected to the turbine in any manner known to those skilled in the art similar to the manner in which alternators are conventionally connected to a crankshaft of an engine, for instance by belt, chain or gears.

The alternator may be spaced from the engine, for instance by more than 25 cm, 50 cm, 1 m, 2 m, etc. In this way, performance and handling of a vehicle may be improved by selecting appropriate location (e.g. weight distribution) of engine system components (such as the engine and the alternator). The turbine may be connected to (e.g. in fluid communication with) the exhaust by an exhaust pipe. In particular, the turbine may be located at substantially any location along an exhaust pipe from the engine, allowing the alternator, and optionally the battery, to be similarly located.

The turbine may be connected to at least one further piece of accessory equipment, including a water pump, an air conditioning compressor, and/or an air pump.

The air pump may be a rotary vane pump, reciprocating (piston) compressor, or any other suitable form of pump or compressor. The air pump may pressurise air up to 600 kpa, 700 kpa, 800 kpa, 850 kpa, 900 kpa or 1 Mpa. The air pump may be constructed from aluminium alloy or any other suitable metal, ceramic, or carbon fibre. The air pump may comprise a non-return valve. The air pump may take in ambient air at a pump inlet and expel pressurised air to the exhaust outlet, or a distinct air outlet, for instance to a propelling nozzle, as described above. In this way, air may be compressed and sent to the exhaust/air outlet to eliminate vortices behind a vehicle in which the engine system is located.

In some embodiments, the air outlet may be connectable to pneumatic tyres of a vehicle in which the engine is located, such that inflation of the tyres may be effected. In particular, a hose may be connectable between the air outlet and the tyres, for instance manually. In some arrangements, the air outlet may be permanently connected to the tyres, and air flow into the tyres may be controllable by a selection switch (which may be manually operable, mechanical, electronic and/or automatic). In some embodiments, the hose may be connectable directly to a propelling nozzle, as described above, for instance via a push-fit connector, screw connector, expanding collar/collet connector or similar connection. In further embodiments, the air pump may be controllable to supply variable air pressures depending on the desired function; for instance, to inflate tyres, to eliminate vortices behind the vehicle and/or to supply air to the engine air intake.

The turbine may be connected to a compressor for delivering compressed gas to the intake, in the manner of a conventional turbocharger. In particular, the compressor may comprise the at least one further piece of accessory equipment, specifically the air pump. The compressor/air pump may have a dual function; specifically, to operate a turbocharger and/or an air outlet. The dual function may comprise a toggle switch for selecting between respective air and/or turbocharger functions, and/or balancing a proportion of pressurised air to be supplied respectively to the turbocharger and/or air outlet.

A metering valve may be provided between the compressor and the intake, to regulate the pressure of gas being provided to the intake. In this way, optimum operation of the engine may be achieved. The metering valve may be computer controlled; however, in alternative embodiments, the metering valve may incorporate some other form of feedback system, for instance a pressure regulated feedback system. The metering valve may comprise a mechanism for diverting a portion of gas from the compressor directly to the exhaust and/or exhaust outlet (i.e. bypassing the engine), which may be enabled in a similar manner to a conventional wastegate.

A pressure relief valve may be incorporated within the system to reduce a level of pressure in excess of a predetermined threshold pressure. The predetermined threshold pressure may be adjustable such that the pressure relief valve may be an adjustable pressure relief valve. Such pressure relief valves may be located at various points throughout the system, for instance immediately before the compressor, immediately after the compressor, immediately before the intake, between the compressor and the intake, immediately after the exhaust, immediately before the turbine, between the exhaust and the turbine, immediately after the turbine, immediately before the exhaust outlet, and/or between the turbine and the exhaust outlet.

After passing through the turbine, exhaust gases may be delivered to an exhaust outlet, which may be located on a rear of a vehicle in which the engine system is incorporated. A check valve may be provided between the turbine and the outlet, in order to regulate the amount of exhaust gas passed to the outlet, and may act as a downstream restrictor that may be controlled to optimise function of the turbine.

In particular, the exhaust/air outlet may comprise a propelling nozzle as described above. For instance, exhaust gasses (or gasses from the air outlet) are converted into a relatively high speed propelling jet by the propelling nozzle. The propelling nozzle may be configured to optimise operation of the turbine by functioning as a downstream restrictor. A vehicle incorporating the engine system described above may further comprise an exhaust outlet connected to the turbine, for removing exhaust gases that have been used to rotate the turbine. The exhaust outlet may be located on a rear of the vehicle such that the exhaust gases are expelled into a turbulent and/or low-pressure region behind the vehicle. In this way, the effect of form drag (due to the shape of the vehicle) can be minimised, by filling the turbulent and/or low-pressure region behind the vehicle with exhaust gases. Any air incident on the front of a vehicle that is taken into the engine (e.g. from a radiator grill) may be expelled immediately behind the vehicle, thereby reducing drag by means of symmetry.

According to a fifth aspect of the present invention, there is provided a method of reducing vehicular drag, the method comprising the steps of: providing a vehicle according to the fourth aspect; and expelling gas from the at least one nozzle substantially toward an interior of the at least one region.

According to a sixth aspect of the present invention, there is provided an engine system of a vehicle, the engine system comprising: an internal combustion engine having an intake and an exhaust; a Pelton wheel turbine of the impulse type connected to the exhaust such that the turbine rotates in response to receiving exhaust gases from the engine; an exhaust outlet to which exhaust gases are delivered after passing through the turbine; an alternator connected to the turbine such that the alternator generates electrical power in response to rotation of the turbine; a propelling nozzle distinct from the exhaust outlet, the propelling nozzle arranged to eject fluid substantially toward an interior of a turbulent and/or low-pressure region behind the vehicle; an air pump connected to the turbine, the air pump configured to take in ambient air at a pump inlet and expel pressurised air to the propelling nozzle; and the propelling nozzle configured such that gasses from the propelling nozzle are converted into a higher speed propelling jet, relative to the speed of the expelled pressurised air from the air pump.

According to a sixth aspect of the present invention, there is provided a method of using energy in exhaust gas from an internal combustion engine, the method comprising the steps of: providing an internal combustion engine of a vehicle having an intake and an exhaust; providing a Pelton wheel turbine of the impulse type connected to the exhaust; rotating the turbine in response to receiving exhaust gases from the engine; delivering the exhaust gases to an exhaust outlet after passing through the turbine; providing an alternator connected to the turbine; generating electrical power with the alternator in response to rotation of the turbine; providing an air pump connected to the turbine; taking in ambient air at a pump inlet of the air pump; providing a propelling nozzle distinct from the exhaust outlet, the propelling nozzle arranged to eject fluid substantially toward an interior of a turbulent and/or low-pressure region behind the vehicle; and expelling pressurised air from the air pump to the propelling nozzle; and converting the expelled pressurised air from the air pump with the propelling nozzle into a higher speed propelling jet, relative to the speed of the expelled pressurised air from the air pump.

BRIEF DESCRIPTION OF THE DRAWINGS

The above and other characteristics, features and advantages of the present invention will become apparent from the following detailed description, taken in conjunction with the accompanying drawings, which illustrate, by way of example, the principles of the invention. This description is given for the sake of example only, without limiting the scope of the invention. The reference figures quoted below refer to the attached drawings.

FIG. 1 is a schematic representation of airflow around the rear of a conventional automobile.

FIG. 2 is a schematic representation of airflow around the rear of the automobile of FIG. 1 incorporating an active drag-reduction system.

FIG. 3 is a schematic representation of an articulated lorry incorporating an embodiment of the present invention.

FIG. 4 is a longitudinal cross section through an outlet of a tip ring nozzle.

FIG. 5 is an end on (axial) view of an outlet of an elliptic sharp tipped shallow lobed nozzle.

FIG. 6 is schematic representation of a typical prior art internal combustion engine and alternator system.

FIG. 7 is a schematic representation of a first engine system arrangement.

FIG. 8 is a schematic representation of a second engine system arrangement.

FIG. 9 is a schematic representation of a third engine system arrangement.

FIG. 10 is a schematic representation of a fourth engine system arrangement.

FIG. 11 is a schematic representation of a fifth engine system arrangement.

FIG. 12 is a schematic representation of a sixth engine system arrangement

DETAILED DESCRIPTION

The present invention will be described with respect to certain drawings but the invention is not limited thereto but only by the claims. The drawings described are only schematic and are non-limiting. Each drawing may not include all of the features of the invention and therefore should not necessarily be considered to be an embodiment of the invention. In the drawings, the size of some of the elements may be exaggerated and not drawn to scale for illustrative purposes. The dimensions and the relative dimensions do not correspond to actual reductions to practice of the invention.

Furthermore, the terms first, second, third and the like in the description and in the claims, are used for distinguishing between similar elements and not necessarily for describing a sequence, either temporally, spatially, in ranking or in any other manner. It is to be understood that the terms so used are interchangeable under appropriate circumstances and that operation is capable in other sequences than described or illustrated herein.

Moreover, the terms top, bottom, over, under and the like in the description and the claims are used for descriptive purposes and not necessarily for describing relative positions. It is to be understood that the terms so used are interchangeable under appropriate circumstances and that operation is capable in other orientations than described or illustrated herein.

It is to be noticed that the term “comprising”, used in the claims, should not be interpreted as being restricted to the means listed thereafter; it does not exclude other elements or steps. It is thus to be interpreted as specifying the presence of the stated features, integers, steps or components as referred to, but does not preclude the presence or addition of one or more other features, integers, steps or components, or groups thereof. Thus, the scope of the expression “a device comprising means A and B” should not be limited to devices consisting only of components A and B. It means that with respect to the present invention, the only relevant components of the device are A and B.

Similarly, it is to be noticed that the term “connected”, used in the description, should not be interpreted as being restricted to direct connections only. Thus, the scope of the expression “a device A connected to a device B” should not be limited to devices or systems wherein an output of device A is directly connected to an input of device B. It means that there exists a path between an output of A and an input of B which may be a path including other devices or means. “Connected” may mean that two or more elements are either in direct physical or electrical contact, or that two or more elements are not in direct contact with each other but yet still co-operate or interact with each other.

Reference throughout this specification to “an embodiment” or “an aspect” means that a particular feature, structure or characteristic described in connection with the embodiment or aspect is included in at least one embodiment or aspect of the present invention. Thus, appearances of the phrases “in one embodiment”, “in an embodiment”, or “in an aspect” in various places throughout this specification are not necessarily all referring to the same embodiment or aspect, but may refer to different embodiments or aspects. Furthermore, the particular features, structures or characteristics of any embodiment or aspect of the invention may be combined in any suitable manner, as would be apparent to one of ordinary skill in the art from this disclosure, in one or more embodiments or aspects.

Similarly, it should be appreciated that in the description various features of the invention are sometimes grouped together in a single embodiment, figure, or description thereof for the purpose of streamlining the disclosure and aiding in the understanding of one or more of the various inventive aspects. This method of disclosure, however, is not to be interpreted as reflecting an intention that the claimed invention requires more features than are expressly recited in each claim. Moreover, the description of any individual drawing or aspect should not necessarily be considered to be an embodiment of the invention. Rather, as the following claims reflect, inventive aspects lie in fewer than all features of a single foregoing disclosed embodiment. Thus, the claims following the detailed description are hereby expressly incorporated into this detailed description, with each claim standing on its own as a separate embodiment of this invention.

Furthermore, while some embodiments described herein include some features included in other embodiments, combinations of features of different embodiments are meant to be within the scope of the invention, and form yet further embodiments, as will be understood by those skilled in the art. For example, in the following claims, any of the claimed embodiments can be used in any combination.

In the description provided herein, numerous specific details are set forth. However, it is understood that embodiments of the invention may be practised without these specific details. In other instances, well-known methods, structures and techniques have not been shown in detail in order not to obscure an understanding of this description.

In the discussion of the invention, unless stated to the contrary, the disclosure of alternative values for the upper or lower limit of the permitted range of a parameter, coupled with an indication that one of said values is more highly preferred than the other, is to be construed as an implied statement that each intermediate value of said parameter, lying between the more preferred and the less preferred of said alternatives, is itself preferred to said less preferred value and also to each value lying between said less preferred value and said intermediate value.

The use of the term “at least one” may mean only one in certain circumstances.

The principles of the invention will now be described by a detailed description of at least one drawing relating to exemplary features of the invention. It is clear that other arrangements can be configured according to the knowledge of persons skilled in the art without departing from the underlying concept or technical teaching of the invention, the invention being limited only by the terms of the appended claims.

FIG. 1 is a schematic representation of airflow around the rear of a conventional automobile 10. Three upper stream-lines 12 are shown passing over the top of the vehicle, and three further lower stream-lines 14 are shown passing underneath the vehicle. Flow separation occurs for the upper streamlines 12 immediately behind the spoiler 16. Similarly, for the lower streamlines 14, flow separation occurs immediately behind the rear wheel 18. Accordingly, for the majority of the view shown, laminar flow is spaced substantially away from the vehicle. A relatively large low pressure/turbulent region 20 is shown immediately behind the vehicle and extending between one and two meters away from the rear of the vehicle.

FIG. 2 is a schematic representation of airflow around the rear of the automobile 10 of FIG. 1 incorporating an active drag-reduction system that comprises an upper row of fluid outlets 22 located immediately below the location of the spoiler 16 (which may be removed), a lower row of fluid outlets 24 located immediately below the bumper/fender 26 and an intermediate row of fluid outlets 28 located on the rear of the vehicle approximately mid-way between the upper 22 and lower 24 rows of fluid outlets.

Air ejected from the upper row of fluid outlets 22 draws (e.g. via Bernoulli's principle and/or the Coanda effect) air flow indicated by the upper stream-lines 12 down such that flow separation is limited. Similarly, air ejected from the lower row of fluid outlets 24 draws air flow indicated by the lower stream-lines 14 upwards, delaying flow separation.

The air ejected from the upper row 22 is relatively low pressure/velocity compared to the air ejected from the lower row 24, as the purpose of the upper row 22 is merely to encourage the Coanda effect around the spoiler. However, the purpose of the lower row 24 is also to fill the lowest pressure part of the low-pressure/turbulent region 20, thereby artificially raising the pressure and/or overcoming the turbulent flow with artificially introduced laminar flow. Thus the air ejected from the lower row 24 is relatively high pressure/velocity compared to the air ejected from the upper row 22.

Air ejected from the intermediate row 28 is provided to smooth the region between the upper row 22 and the lower row 24, and is therefore at a pressure/speed between that of the upper and lower ejected air flows. In smaller cars such as coupes, the intermediate row 28 could be dispensed with. In larger vehicles such as lorries, there may be more than one intermediate row 28 to allow a more gradual variation in injected air flow speed/pressure.

FIG. 3 is a schematic representation of an articulated lorry 180 incorporating an active drag reduction system 205. The lorry 180, when travelling forwards, suffers from drag, in particular form drag due to the substantially un-streamlined shape of the vehicle. Vortices 190 are formed in a low-pressure region behind the lorry 180, which contribute substantially to the form drag. The form drag could be reduces by streamlining the rear of the lorry 180; however, such an approach is undesirable because of the desire for the vehicle to allow easy access to its contents. Upper outlets 200 are provided on a periphery of the rear of the vehicle, and are specifically directed at the boundary 195 of the vortex behind the vehicle. Intermediate outlets 210 are provided on the rear of the vehicle spaced from the periphery, and are specifically directed into the low-pressure region behind the vehicle, in order to minimise drag by reducing vortices and thereby reducing resistance. Lower outlets 200 are also provided. These outlets are preferably nozzles of the form described above. In particular, the first outlets may be a convergent nozzles and/or a nozzles supplying relatively high temperature air, and the second outlets may be divergent nozzles and/or nozzles supplying relatively low temperature air. The figure shows two such outlets of each kind 200, 210; however, a single outlet, or multiple outlets (e.g. 3, 4, 5, 6, 10, 20, etc.) of each kind are also envisaged. Device 215 may provide gas to each of the nozzles 200 and 210 for expulsion into vortices 190.

In some arrangements, the outlets may be located between the cabin of the articulated lorry 180 and the container body, or adjacent to any low pressure region and/or vortex produced by a similar moving vehicle, such as behind wheels. In further arrangements, the outlets may be located on a spoiler, or adjacent to a spoiler. In particular, the outlets on/adjacent to a spoiler may be convergent nozzles and/or a nozzles supplying relatively high temperature air. An actuator and force amplifier assembly may be incorporated (e.g. adjacent to the spoiler), which may receive compressed air at a first pressure and convert it to a different pressure in accordance with Pascal's law.

In some embodiments, the nozzle arrangement may be reversed such that relatively high temperature air is expelled into a high pressure region in front of the vehicle, which may be present due to ram forces. The relatively high temperature air may warm the high pressure region, encouraging it to expand and dissipate, thereby reducing form drag. In particular, in some specific embodiments, the nozzles may be directed toward relatively high pressure regions adjacent to the vehicle.

FIG. 4 is a longitudinal cross section through an outlet of a tip ring nozzle 1, having an annular band 2 located around the interior of the outlet of the nozzle, the annular band 2 having an approximately circular cross section, and being curved around on itself to form a substantially toroidal shape. The arrow 3 indicated direction of flow of gas through the divergent part of the nozzle. Preceding parts of the nozzle (for instance, a convergent section) are not shown for clarity.

FIG. 5 is an end on (axial) view of an outlet of an elliptic sharp tipped shallow lobed nozzle 4. The nozzle 4 has an interior profile 5 in the form of four equally spaced lobes, each separated by a sharp wall 6. The inlet 7 of the nozzle 4 is shown as an opening of reduced diameter, which may form the throat of the nozzle. The inlet 7 may comprise the connection between a converging portion of the nozzle (not shown) and the diverging portion of the nozzle 4. Therefore, the skilled person will appreciate that the degree by which the cross section of the nozzle differs from circular increases from the inlet 7 to the outlet interior profile 5.

FIG. 6 is schematic representation of a typical prior art internal combustion engine and alternator system. An internal combustion engine is provided with a cylinder 1000, a reciprocating piston 2000 therein, an intake 30, an intake valve 40 (for controlling flow of gas into the engine through the intake 1000), an exhaust 50, and an exhaust valve 60 (for regulating flow of exhaust gas out of the engine through the exhaust 50).

Operation of the internal combustion engine, the details of which are not shown for clarity, causes the piston to reciprocate, thereby rotating a crankshaft 70. Rotation of the crankshaft 70 is used to drive a belt 80 which in turn operates alternator 90 via alternator pulley 100. The alternator pulley 100 is sized relative to the crankshaft 70 such that a higher rpm is provided at the alternator 90 that is present at the crankshaft 70. That is, the piston 2000 must do work operating the alternator 90.

FIG. 7 is a schematic representation of a first embodiment of the present invention in which the prior art shown in FIG. 6 is modified in the following way. A turbine 110 is placed at the exhaust 50 such that exhaust gases from the engine rotate the turbine. Subsequently, such gases may leave the turbine via the exhaust outlet 120. The belt 80 is coupled to an axle of the turbine 110, rather than to the crankshaft 70, thereby reducing the load on the piston 2000. The alternator 90 is driven by the belt 80, via the alternator pulley 100 as before.

However, the turbine 110 is constructed to provide a rotational speed suitable for the alternator 90, such that gearing provided by selecting suitably sized pulleys for use with the belt 80 are not required. In an alternative embodiment, it is envisaged that the alternator 90 could be connected directly to the axle of the turbine 110, foregoing the need for the belt 80 and alternator pulley 100.

FIG. 8 is a schematic representation of a second embodiment of the present invention, which is a further modification of the first embodiment shown in FIG. 7. In this arrangement, the belt 80 drives the alternator 90 and additionally a further accessory device 130, such as an air conditioning compressor unit. A further accessory device 140 is driven by a further belt 150, also on the axle of the turbine 110. The further accessory device 140 could be a water pump, for example; however, any other component that would more typically be driven directly by the crankshaft.

FIG. 9 is a schematic representation of a third embodiment of the present invention, which is an alternative or additional modification of the first embodiment shown in FIG. 7. The axle of the turbine 110 is made in common with an axle of a compressor 160 located at the intake, as is conventional in turbocharging devices. As in the other embodiments, the alternator 90 is driven by the axle of the turbine 110. A metering valve 170 is located between the compressor 160 and the intake valve 40 and is configured to direct a gas flow from the compressor away from the intake valve 40, in the event that the compression provided by the compressor exceeds some threshold amount. In some embodiments, the diverted gas 180 is conveyed to the exhaust outlet 120, or to other outlets such as the propelling nozzles discussed above. The metering valve 170 may divert all or none of the gas from the compressor 160, or any proportion therebetween.

Although exhaust gas may be conveyed to the propelling nozzles of the present invention, it is preferable that exhaust gas is simply expelled in a conventional manner. Gas from another source may be provided to the nozzles. In particular, exhaust gas would be useful because it is both hot and at relatively high temperature; however, it may also contain relatively large amounts of unburned hydrocarbons and other impurities, which could cause the nozzles to block/clog over time, or at least reduce their efficiency. It is therefore desirable to use the heat and/or pressure of the exhaust gas to provide suitable air flow through the propelling nozzle(s) of the present invention. For example, a heat exchanger could be used to reclaim waste heat, and/or a turbo expander could be used to extract pressure for re-use. The exhaust gas could then be passed to a silencer and/or exhaust pipe exit.

FIG. 10 is a schematic representation of a fourth embodiment of the present invention, in which an air compressor 140 is driven by the turbine 110 to produce a stream of compressed air (or other gas) that flows down a pipe 300. The air compressor 140 may take air from ambient, or in alternative embodiments may take air from the engine inlet via metering valve 170. The compressor may be, for instance, a vane type compressor.

This air compressed by the air compressor 140 may be supplied directly to the propelling nozzles and/or may be sent to a vortex tube 310 that splits the steam into a relatively high temperature stream that may be sent to a propelling nozzle via valve 320 and a relatively low temperature stream that may be sent to a propelling nozzle via valve 340. Optionally, a heater and/or cooler 330 may be placed in-line with either the hot stream or the cold stream, or exceptionally to the compressed air stream prior to its introduction into the vortex tube 310. A further check valve 350 may also be included in the pipe 300. Each check valve shown in the drawings may optionally be accompanied or replaced by a pressure sensor. A controller may be configured to operate the or each check valve in response to pressure measured by the pressure sensor(s). A fuel control unit may be associated with the or each pressure sensor and/or check valve.

It is to be appreciated that the arrangement in FIG. 10 could be modified such that the air compressor 140 is driven by the crankshaft 70, rather than via a turbine 110, in a configuration similar to that show in FIG. 6.

FIG. 11 is a schematic representation of a fifth embodiment of the present invention in which air flow from the metering valve 170 (compressed by the compressor 160) is supplied directly to the propelling nozzles via pipe 360 (conveying relatively cold air), and/or to a heat exchanger 380 via a check valve 370. The heat exchanger 380 may be configured to remove heat from the exhaust gases within the exhaust pipe 120 to warm the compressed air from the check valve 370 in order to provide a relatively high temperature stream 390 to a propelling nozzle, as described above.

FIG. 12 is a schematic representation of a sixth embodiment of the present invention in which compressed air is taken from the metering valve 170 as in FIG. 11, but is conveyed to a vortex tube 310 as in FIG. 10. In particular, a cooler 330 is provided in the pipe 300 prior to the vortex tube 310.

Any combination of the above embodiments may be used to create a system having some or all of the advantages described above.

Claims

1. An active drag-reduction system for a vehicle in which at least one turbulent and/or low-pressure region is formed adjacent to the vehicle when moving at a speed above a predetermined threshold speed, the active drag-reduction system configured to reduce the at least one turbulent and/or low-pressure region when activated, the active drag-reduction system comprising:

at least one propelling nozzle located adjacent to the at least one region and arranged to eject fluid substantially toward an interior of the at least one region; and

a device for providing gas to the at least one nozzle for expulsion into the at least one region;

wherein the at least one propelling nozzle comprises a tip ring supersonic nozzle and/or elliptic sharp tipped shallow lobed nozzle.

2. A vehicle configured such that, when moving at a speed above a predetermined threshold speed, at least one turbulent and/or low-pressure region is formed adjacent to the vehicle, the vehicle comprising an engine system comprising:

an internal combustion engine having an intake and an exhaust;

a turbine connected to the exhaust such that the turbine rotates in response to receiving exhaust gases from the engine;

an alternator connected to the turbine such that the alternator generates electrical power in response to rotation of the turbine; and

an exhaust outlet connected to the turbine, for removing exhaust gases that have been used to rotate the turbine, the exhaust outlet comprising a propelling nozzle located on a rear of the vehicle such that the exhaust gases are expelled substantially toward an interior of a turbulent and/or low-pressure region behind the vehicle;

wherein the exhaust provides gas directly to the nozzle.

3. A method of reducing vehicular drag, the method comprising the steps of:

providing a vehicle according to claim 2; and

expelling gas from the at least one nozzle substantially toward an interior of the at least one region.

4. An engine system of a vehicle, the engine system comprising:

an internal combustion engine having an intake and an exhaust;

a Pelton wheel turbine of the impulse type connected to the exhaust such that the turbine rotates in response to receiving exhaust gases from the engine;

an exhaust outlet to which exhaust gases are delivered after passing through the turbine;

an alternator connected to the turbine such that the alternator generates electrical power in response to rotation of the turbine;

a propelling nozzle distinct from the exhaust outlet, the propelling nozzle arranged to eject fluid substantially toward an interior of a turbulent and/or low-pressure region behind the vehicle;

an air pump connected to the turbine, the air pump configured to take in ambient air at a pump inlet and expel pressurised air to the propelling nozzle; and

the propelling nozzle configured such that gasses from the propelling nozzle are converted into a higher speed propelling jet, relative to the speed of the expelled pressurised air from the air pump.

5. The engine system of claim 4, wherein the air pump is a reciprocating piston compressor.

6. The engine system of claim 4, wherein the alternator is spaced from the engine by more than 25 cm.

7. The engine system of claim 4, further comprising:

a compressor connected to the turbine such that the compressor rotates in response to rotation of the turbine, wherein the compressor is arranged to compress gas for delivery to the intake; and

a metering valve, provided between the compressor and the intake, configured to regulate the gas pressure provided to the intake.

8. A method of using energy in exhaust gas from an internal combustion engine, the method comprising the steps of:

providing an internal combustion engine of a vehicle having an intake and an exhaust;

providing a Pelton wheel turbine of the impulse type connected to the exhaust;

rotating the turbine in response to receiving exhaust gases from the engine;

delivering the exhaust gases to an exhaust outlet after passing through the turbine;

providing an alternator connected to the turbine;

generating electrical power with the alternator in response to rotation of the turbine;

providing an air pump connected to the turbine;

taking in ambient air at a pump inlet of the air pump;

providing a propelling nozzle distinct from the exhaust outlet, the propelling nozzle arranged to eject fluid substantially toward an interior of a turbulent and/or low-pressure region behind the vehicle; and

expelling pressurised air from the air pump to the propelling nozzle; and

converting the expelled pressurised air from the air pump with the propelling nozzle into a higher speed propelling jet, relative to the speed of the expelled pressurised air from the air pump.

9. A vehicle configured such that, when moving at a speed above a predetermined threshold speed, at least one high pressure region is formed adjacent to the vehicle, the vehicle comprising:

at least one propelling nozzle located adjacent to the at least one region; and

a system for providing gas to the at least one nozzle for expulsion into the at least one region.

10. The vehicle of claim 9, wherein the gas is provided at a relatively high temperature.

11. A method of reducing vehicular drag, the method comprising the steps of:

providing a vehicle according to claim 9; and

expelling gas from the at least one nozzle into the at least one region.