The present disclosure relates to an integrated forced-induction and heat exchanger apparatus, a method of operating such an apparatus, a system comprising an engine and the aforementioned apparatus, and a vehicle comprising the apparatus or the aforementioned system. The integrated forced-induction and heat exchanger apparatus may have applications in automotive and/or motorsport systems, such as internal combustion piston engines, as well as aerospace systems.

INTRODUCTION

In internal combustion piston engines, forced induction (e.g. turbocharging and supercharging) is frequently used to improve engine performance. By pressurising the charge air entering the engine cylinders during the intake stroke, more fuel can be combusted and power obtained from the engine as a higher mass of air is present. Forced induction engines generally make use of an intercooler to cool the charge air after compression and before it enters the engine cylinders. The resultant lower temperature of the cooled charge air both increases the density of the charge air, enabling more air to enter the cylinders, and has other technical benefits such as reducing engine temperatures and preventing premature combustion, known as detonation or knock.

Existing intercooler designs are typically generally cuboid in form, and utilise substantially straight flow passages. Plate and fin type heat exchangers are widely used as intercoolers, but these generally have low heat transfer coefficients, necessitating relatively large heat exchangers to obtain the required heat transfer coefficient. Typically, the heat exchangers are fluidly connected with ducting between the compressor outlet and engine cylinder inlets. In a turbocharger arrangement, the volume of air between the compressor outlet and the engine cylinder inlets is proportional to the time delay between the speed of a compressor increasing, driven by the exhaust of the engine, and the pressurised charge air reaching the cylinders. This delay is generally known as ‘turbo lag’ and is highly undesirable in engines which require a rapid change in power output, such as those used in automotive and/or motorsport applications.

The present disclosure seeks to address and/or at least ameliorate to a certain degree the problems associated with the prior art.

SUMMARY

According to a first aspect of the disclosure, there is provided an integrated forced-induction and heat exchanger apparatus comprising: a heat exchanger arrangement for carrying a first heat transfer medium, the heat exchanger arrangement being generally annular in form with an axial aperture therethrough; and a compressor arranged at least partially within said axial aperture for compressing and delivering a second heat transfer medium over said heat exchanger arrangement.

Advantageously, an arrangement of the compressor at least partially within the axial aperture of the heat exchanger arrangement allows for a compact configuration. The overall volume of the apparatus can be reduced and the arrangement can improve the packaging of a wider system comprising the apparatus and an engine. Improving the packaging of a wider system may have the additional benefit of reducing the expansion and contraction of compressed fluid between a compressor exit and engine cylinder inlets. In addition, with such an arrangement, the flow passages between the compressor and the heat exchanger arrangement may be minimised, to reduce the volume after the compressor which can delay the supply of compressed fluid to the heat exchanger arrangement and subsequently to an engine to which the apparatus may be fluidly coupled. In certain conditions, this delay may be known as turbo lag. Reducing the delay in the supply of compressed fluid to an engine to which the apparatus may be fluidly coupled is highly desirable in applications which require frequent changes in power output such as automotive and/or motorsport applications.

Advantageously, the annular form of the heat exchanger arrangement provides for a relatively large heat transfer surface or surfaces.

The heat exchanger apparatus may be substantially tubular in overall form. The rotational axis of the compressor may be coincident with the rotational axis of the heat exchanger arrangement.

The terms longitudinal and axial may be used interchangeably throughout this specification. Any radial direction is defined in relation to a longitudinal direction parallel with any longitudinal axis disclosed throughout this specification, for example the central longitudinal axis of the apparatus.

Optionally, the integrated forced-induction and heat exchanger apparatus further comprises a casing comprising a first side and a second side, the second side of said casing having a larger cross-dimension than an equivalent cross-dimension of the first side of said casing. Advantageously, a casing comprising a second side with a larger cross-dimension than an equivalent cross-dimension of the first side of said casing follows closely the form of the heat exchanger arrangement.

The casing may form the walls of flow channels within the apparatus, for example, the flow channels between the compressor and the heat exchanger arrangement. Advantageously, the configuration of the casing can serve to minimise the materials needed and the overall form of the apparatus.

Advantageously, this shape of the casing allows for the flow of the second heat transfer medium to be turned efficiently, reducing pressure drop of the fluid and overall size of the casing. This assists in reducing the volume of second heat transfer medium within the apparatus at any one time which contributes to reducing the delay in the supply of compressed fluid to an engine to which the apparatus may be fluidly coupled. Furthermore, this shape of the casing assists in maximising the flow uniformity of the second heat transfer medium.

The casing may be formed generally as a frustum. The casing may be a frustum of a cone, for example when the heat exchanger arrangement is formed generally as a tube. Alternative forms of casing are also envisaged, for example, a frustum of a pyramid.

Optionally, the heat exchanger arrangement comprises a plurality of tubes for carrying said first heat transfer medium.

Advantageously, a plurality of tubes provides for multiple heat transfer surfaces and can thereby improve the efficiency of the heat exchanger arrangement.

Such a heat exchanger arrangement may be a shell and tube type heat exchanger. However, other heat exchanger arrangements are also possible. For example, the heat exchanger arrangement may be a plate heat exchanger, a double-pipe heat exchanger, or a two-phase heat exchanger such as a condenser or a boiler.

The each of the plurality of tubes may have a first end and a second end.

Optionally, the plurality of tubes are arranged generally as an involute spiral.

Advantageously, tubes arranged generally as an involute spiral allows for a large number of tubes to be arranged together providing a large heat exchanger surface for the volume and allowing the volume of the heat exchanger arrangement to be reduced and thus the volume of the second heat transfer medium in the apparatus to be reduced. The tubes may be nested to increase the density of the heat transfer surfaces for the volume. This can contribute to the reduction of the delay in the supply of compressed fluid to an engine to which the apparatus may be fluidly coupled.

When the plurality of tubes are arranged generally as an involute spiral, the plurality of tubes may follow a spiral path. The spiral path of the plurality of tubes can be generally circular, generally elliptical, or generally polygonal. When arranged generally as an involute spiral, the plurality of tubes may comprise a plurality of generally straight sections and/or one or more generally curved sections.

However, the plurality of tubes may also be arranged in a different way. For example, the tubes may extend generally longitudinally, e.g. substantially parallel to the central longitudinal axis of the apparatus or generally radially. At least one end plate may be provided for fluidly coupling at least two of the plurality of tubes. At least one end plate may be generally annular in form, or may form part of an annulus. At least one end plate may be formed as one continuous chamber or may comprise two or more chambers or segments which together can form a generally annular end plate. The segments may not form a continuous flow channel. At least one end plate may define a turning volume for turning the first heat transfer medium. At least one end plate may be arranged at a first side of the apparatus. At least one end plate may be arranged closer to a second side of the apparatus than the first side of the apparatus. If there are two or more end plates, two or more end plates may be formed as one integral part.

Each tube in the plurality of tubes may each have an outer cross-dimension of generally less than 1 millimetre.

Optionally, the integrated forced-induction and heat exchanger apparatus further comprises an annular inlet manifold fluidly coupled to the heat exchanger arrangement for delivering the first heat transfer medium thereto.

Advantageously, an annular inlet manifold can allow for the inlet manifold to maximise the surface area of its interface with the heat exchanger arrangement, reducing pressure drop of the first heat transfer medium when delivered to the heat exchanger arrangement and allowing for components to be arranged in a more space-efficient manner. Reducing pressure drop of the first heat transfer medium may improve the heat transfer coefficient of the apparatus. An improvement of the heat transfer coefficient may allow for the volume of the heat exchanger arrangement to be reduced and thus the volume of the second heat transfer medium in the apparatus to be reduced. This can allow the apparatus to be generally more compact, reducing the mass of the casing due to its reduction in size. Further, this can also contribute to the reduction of the delay in the supply of compressed fluid to an engine to which the apparatus may be fluidly coupled. The inlet manifold may be formed as one continuous chamber or may comprise two or more chambers or segments which together can form a generally annular manifold. The segments may not form a continuous flow channel. The inlet manifold may be arranged at a first side of the apparatus.

The inlet manifold may further comprise an inlet manifold inlet. The inlet manifold inlet may extend generally longitudinally.

The inlet manifold may be coupled to the heat exchanger arrangement via one or more inlet headers. The inlet headers may be coupled to at least one of the plurality of tubes. The inlet headers may be coupled to a first end of at least one of the plurality of tubes. The inlet headers may extend generally longitudinally.

Optionally, the integrated forced-induction and heat exchanger apparatus further comprises an annular outlet manifold fluidly coupled to the heat exchanger arrangement for receiving the first heat transfer medium therefrom.

Advantageously, the annular outlet manifold can serve to maximise the surface area of its interface with the heat exchanger arrangement, reducing pressure drop of the first heat transfer medium when received from the heat exchanger arrangement and allowing for components to be arranged in a more space-efficient manner. The outlet manifold may be formed as one continuous chamber or may comprise two or more chambers or segments which together can form a generally annular manifold. The segments may not form a continuous flow channel. The outlet manifold may be arranged at the first side of the apparatus.

The outlet manifold may further comprise an outlet manifold outlet. The outlet manifold outlet may extend generally longitudinally.

The outlet manifold may be coupled to the heat exchanger arrangement via one or more outlet headers. The outlet headers may be coupled to at least one of the plurality of tubes. The outlet headers may be coupled to a second end of at least one of the plurality of tubes. The outlet headers may extend generally longitudinally.

Optionally, the inlet and outlet manifolds are arranged on a common side of the apparatus.

Advantageously, arranging the inlet and outlet manifold on a common side may facilitate manufacture of the apparatus and allows for components of the apparatus to be arranged in a more space-efficient manner and to reduce the size and weight of the apparatus.

The inlet and/or the outlet manifolds and/or at least one end plate may be generally aligned. The inlet and/or outlet manifolds and/or at least one end plate may share the same central longitudinal axis, and thus be concentric. Each of the inlet and/or outlet manifolds and/or at least one end plate may share the same central longitudinal axis as the axial aperture of the heat exchanger arrangement. Further, at least one end plate may be arranged substantially between the inlet and outlet manifolds. The inlet manifold and/or the outlet manifold and/or at least one end plate may be formed as one integral part.

Optionally, the heat exchanger arrangement is arranged, at least in part, axially before or in front of the compressor inlet with respect to the central longitudinal axis. The heat exchanger arrangement is though fluidly coupled downstream of the compressor. For example, the heat exchanger arrangement may be arranged, at least in part, relatively nearer an upstream side of the integrated forced-induction and heat exchanger apparatus than the compressor. Such an arrangement can allow for a space-efficient arrangement of the components.

Optionally, the heat exchanger arrangement substantially overlaps the compressor.

Advantageously, an overlapping arrangement allows for the components of the apparatus to be arranged in a more space-efficient manner and to reduce the size and weight of the apparatus. Reducing the volume of the apparatus further assists in the reduction of the delay in the supply of compressed fluid to an engine to which the apparatus may be fluidly coupled.

With respect to the central longitudinal axis of the apparatus, the heat exchanger arrangement may overlap with the compressor. The heat exchanger arrangement may partially enclose the compressor. The compressor may be arranged partially within the heat exchanger arrangement. The heat exchanger arrangement may have an inner surface. The inner surface of the heat exchanger arrangement may be a lateral inner surface of the heat exchanger arrangement, extending generally longitudinally. The heat exchanger arrangement may have an outer surface. The outer surface of the heat exchanger arrangement may be a lateral outer surface of the heat exchanger arrangement, extending generally longitudinally. The outer surface of the heat exchanger arrangement may share the same rotational axis as the axial aperture of the heat exchanger arrangement. A portion of the compressor may be arranged outside of the axial aperture of the heat exchanger arrangement.

Optionally, the compressor is arranged substantially or fully within the axial aperture of the heat exchanger arrangement.

Advantageously, the arrangement of the compressor substantially or fully with the axial aperture of the heat exchanger arrangement allows for the components of the apparatus to be arranged in a spaceefficient manner and can serve to reduce the size and weight of the apparatus. Reducing the volume of the apparatus can further assist in the reduction of the delay in the supply of compressed fluid to an engine to which the apparatus may be fluidly coupled.

More than 25% of the compressor may be arranged within the axial aperture of the heat exchanger arrangement, for example more than 50%, more than 75%, more than 85%, more than 95%, or substantially 100%.

The compressor may further comprise a flow inlet, an impeller, and an impeller housing. The flow inlet, and/or the impeller, and/or the impeller housing may be arranged substantially or fully within the axial aperture of the heat exchanger arrangement.

The flow inlet may further comprise a first portion and a second portion. The first portion is for conveying the incoming flow of the second heat transfer medium and turning it longitudinally. The first portion may comprise one or more sub-inlets. The sub-inlets may each convey separate incoming flows of the second heat transfer medium, which may then be combined in the first portion. The first portion and the second portion may each be oriented in any direction. The first and second portions may each be oriented one of radially or longitudinally and may extend substantially perpendicularly to one another. The first and second portions are fluidly coupled and may be configured for turning the second heat transfer medium radially to longitudinally or vice versa.

The impeller may be arranged substantially within the impeller housing.

Optionally, the compressor is one of an axial compressor and a centrifugal compressor. Advantageously, an axial or centrifugal compressor allows for higher compression efficiencies, a simpler construction than other compressor types, and a more space-efficient compressor and can reduce the size and weight of the apparatus. Reducing the volume of the apparatus can further assist in the reduction of the delay in the supply of compressed fluid to an engine to which the apparatus may be fluidly coupled.

The compressor may be driven by a shaft. The shaft may be either mechanically driven by an engine, as in a supercharger arrangement for example, or driven by an exhaust fluid of an engine, as in a turbocharger arrangement for example.

The compressor may be a positive displacement compressor, or may be a dynamic compressor. Dynamic compressors may include an axial or centrifugal compressor. An axial compressor may further comprise at least one array of airfoils, including, for example, rotors and stators. An axial compressor may comprise a combination of rotors and stators. A centrifugal compressor may further comprise an impeller further comprising at least one blade. Each of the impeller blades may be open, semi-open, or covered, and partial or full blades. Furthermore, each of the impeller blades may include backsweep to improve efficiencies.

Optionally, the integrated forced-induction and heat exchanger apparatus further comprises a circumferential radially extending flow outlet from said compressor.

The flow outlet may be aligned generally with an exit of the compressor. More specifically, the flow outlet may be aligned with the impeller housing. The flow outlet may be a diffuser. The flow outlet may form one continuous volume or may comprise separate segments. The flow outlet may be disc-shaped. The flow outlet may be annular in form. The flow outlet may form an incomplete annulus.

Optionally, the integrated forced-induction and heat exchanger apparatus comprises an inlet turning vane for turning the second heat transfer medium from said circumferential radially extending flow outlet from radial to longitudinal and back to radial across the heat exchanger arrangement. The flow passages from the outlet of the compressor can be arranged to turn the flow opposite to the inlet flow to the compressor. This can allow a more compact configuration.

Advantageously, the inlet turning vane assists the turning of flow of the second heat transfer medium, allowing for improved uniformity and reducing pressure drop. Increasing an outer cross dimension of the heat exchanger arrangement has a much greater effect on the dynamic head of the flow at an outer surface of the heat exchanger arrangement than increasing a cross dimension of the axial aperture of the heat exchanger arrangement by the same amount does on the dynamic head of the flow at an inner surface of the heat exchanger arrangement, said inner surface of the heat exchanger arrangement defining the boundary of the axial aperture.

As increasing an outer cross dimension of the heat exchanger arrangement has a much greater effect on the dynamic head of the flow at an outer surface of the heat exchanger arrangement, when designing the heat exchanger arrangement to reduce pressure drop of the second heat transfer medium flowing over it, the dynamic head at the outer surface of the heat exchanger arrangement can be reduced more effectively than the dynamic head at the inner surface of the heat exchanger arrangement. Thus, when taking into account packaging constraints, the dynamic head in the longitudinal flow at the outer surface of the heat exchanger arrangement is often much lower than the dynamic head of the longitudinal flow at the inner surface of the heat exchanger.

Turning the second heat transfer medium where the dynamic head of the axial flow is lower, e.g. at the outer surface of the heat exchanger arrangement, reduces the overall pressure losses of the flow due to turning. A reduction in turning losses allows either a reduction in the overall system pressure drop, increasing the output charge pressure of the second heat transfer medium, and/or an increase in the allowable pressure drop across the heat exchanger arrangement which generally results in a higher heat transfer coefficient. This results in a more compact apparatus with a lower mass than would otherwise be possible.

The flow outlet from the compressor may be arranged adjacent a second side of the apparatus, and may be adjacent a radially extending first outer wall of the apparatus which may be arranged at a second side of said apparatus. A first turning flow channel, where flow may be turned from radial to longitudinal and back to radial across the heat exchanger arrangement, may be arranged adjacent an outer surface of the heat exchanger arrangement, and may be coupled to the flow outlet from the compressor. The first turning flow channel may be arranged substantially between an outer surface of the heat exchanger arrangement and a second outer wall of the apparatus. The second outer wall of the apparatus may extend in a direction with both longitudinal and radial components, and may be coupled to the first outer wall of the apparatus. The first turning flow channel has a first cross-dimension taken in a radial plane at a first side of the apparatus, and a second cross-dimension taken in a radial plane closer to a second side of the apparatus. The second cross-dimension of the first turning flow channel may be larger than the first cross-dimension of the first turning flow channel. The inlet turning vane may be arranged substantially within the first turning flow channel. The first turning flow channel may be adjacent at least one inlet header and/or at least one outlet header.

The inlet turning vane may have an arcuate profile and may be an annular ring. There may be more than one turning vane, such as two, three, or four. The inlet turning vane may form an incomplete annulus. The inlet turning vane may be a circular or substantially circular ring. The inlet turning vane may have a substantially constant thickness between a leading edge and a trailing edge thereof, other than any streamlining curvature at a leading edge and/or a trailing edge thereof.

The second heat transfer medium may flow generally radially inward across the heat exchanger arrangement, towards the central longitudinal axis of the apparatus, or the second heat transfer medium may flow generally radially outward across the heat exchanger arrangement, away from the central longitudinal axis of the apparatus. The inlet turning vane may be arranged substantially outside of the axial aperture of the heat exchanger arrangement.

Optionally, the inlet turning vane extends circumferentially. Optionally, the integrated forced-induction and heat exchanger apparatus further comprises one or more exit turning vanes for turning the second heat transfer medium from radial to longitudinal after said heat exchanger arrangement.

Advantageously, the exit turning vanes improve flow uniformity of the second heat transfer medium through the heat exchanger arrangement. Furthermore, the exit turning vanes reduce pressure drop of the second heat transfer medium after the heat exchanger arrangement. Both of these advantages facilitate a reduction in the overall system pressure drop, increasing the output charge pressure of the second heat transfer medium, and/or an increase in the allowable pressure drop across the heat exchanger arrangement which generally results in a higher heat transfer coefficient. This results in a more compact apparatus with a lower mass than would otherwise be possible.

A second turning flow channel, where flow from across the heat exchanger arrangement may be turned from radial to longitudinal, may be arranged adjacent the inner surface of the heat exchanger arrangement, and may be coupled to the first turning flow channel. The second turning flow channel may be arranged substantially between an inner surface of the heat exchanger arrangement and the compressor. The second turning flow channel may be generally annular in form. The exit turning vane may be arranged substantially within the second turning flow channel. The second turning flow channel may be adjacent at least one inlet header and/or at least one outlet header.

The exit turning vane may have an arcuate profile and may be an annular ring. There may be more than one exit turning vane, such as two, three, or four. The exit turning vane may form an incomplete annulus. The exit turning vane may be a circular or substantially circular ring. The exit turning vane may have a substantially constant thickness between a leading edge and a trailing edge thereof, other than any streamlining curvature at a leading edge and/or a trailing edge thereof.

There may be two or more exit turning vanes, such as two, three, four, or five exit turning vanes. Common parts of the two or more exit turning vanes may be arranged at different distances from the heat exchanger arrangement. The common parts may be leading or trailing edges of the vanes. The two or more exit turning vanes may be concentric about a central longitudinal axis of the apparatus, and may be concentric about a central longitudinal axis of the axial aperture of the apparatus. The two or more exit turning vanes may be interested with one another, at least in a sense that a section taken perpendicular to a central longitudinal axis of the heat exchanger a leading or trailing edge of one exit turning vane is overlapped with an adjacent exit turning vane.

Optionally, the integrated forced-induction and heat exchanger apparatus further comprises a circumferential air exit volute for said second heat transfer medium.

Advantageously, this allows for the air exit volute to maximise the surface area of its interface with the volume after the heat exchanger arrangement, reducing pressure drop of the second heat transfer medium when delivered from the heat exchanger arrangement and allowing for components to be arranged in a more space-efficient manner. This allows either a reduction in the overall system pressure drop, increasing the output charge pressure of the second heat transfer medium, and/or an increase in the allowable pressure drop across the heat exchanger arrangement which generally results in a higher heat transfer coefficient. This results in a more compact apparatus with a lower mass than would otherwise be possible.

The air exit volute may be arranged at the first side of the apparatus. The air exit volute may be arranged substantially around the compressor. The air exit volute may be coupled to the second turning flow channel and may be generally annular in form. The air exit volute may further comprise an air exit volute housing. The air exit volute may be bounded by the air exit volute housing and the compressor. The exit turning vane may be arranged at least partially within the air exit volute.

Optionally, the flow outlet from the compressor abuts the heat exchanger arrangement.

Advantageously, this allows for the components of the apparatus to be arranged in a more spaceefficient manner and to reduce the size and weight of the apparatus. Reducing the volume of the apparatus further assists in the reduction of the delay in the supply of compressed fluid to an engine to which the apparatus may be fluidly coupled.

In some embodiments, the heat exchanger arrangement, compressor, and casing are each at least partly made of an alloy material, such as stainless steel, a Nickel alloy, an Aluminium alloy, a ceramic alloy, or a heat-resistant alloy.

The heat exchanger arrangement may be manufactured using an additive manufacturing technique.

Optionally, the apparatus may comprise two or more compressors, which may be arranged back to back.

Advantageously, this allows for the compressors to compress the second heat transfer medium more efficiently given packaging constraints and reduces pressure losses. Furthermore, such an arrangement may reduce the net axial thrust force acting on the shaft and other components relating to the forced induction, in turn reducing stress experienced by said components, as the axial thrust force generated by each compressor may be equally opposed and balanced out by a corresponding force of one of the other compressors. Each of the plurality of compressors may comprise at least one flow inlet, an impeller, an impeller housing, and a shaft. The plurality of compressors may share an impeller housing and/or shaft. The direction of each flow inlet may be substantially the same and/or substantially parallel and/or substantially orthogonal.

Optionally, the heat exchanger may comprise a plurality of heat exchanger stages, for example two or three.

Advantageously, this may facilitate the cooling of relatively hot (e.g. 300C at 6 bar) fluid from the compressor outlet and reduce the likelihood of boiling of the first heat transfer medium acting as a coolant, whilst allowing the volume of the heat exchanger arrangement to be reduced and thus the volume of the second heat transfer medium in the apparatus to be reduced.

Each of the plurality of heat exchanger stages may comprise an inlet manifold, an outlet manifold, at least one inlet header, at least one outlet header, and a plurality of tubes.

Optionally, the plurality of tubes of each heat exchanger stage may be arranged generally as an involute spiral, or may extend generally longitudinally, with at least one end plate provided for fluidly coupling at least two of said tubes.

Optionally, the stages may be arranged about a central longitudinal axis of the apparatus. The stages may each have an axial aperture defined therethrough, said stages and axial apertures sharing the same central longitudinal axis as the apparatus. At least one of the stages may be arranged at least partially within the axial aperture of at least one other stage.

The inlet and outlet manifolds of the stages may be arranged on a common side of the apparatus, may be generally aligned, may be generally concentric, and may share the same central longitudinal axis as an axial aperture of one of the stages.

According to a second aspect of the disclosure, there is provided a method of cooling a fluid using an integrated forced-induction and heat exchanger apparatus according to a first aspect of the disclosure and any optional feature thereon, including the steps of: supplying a first heat transfer medium to said tube arrangement; supplying a second heat transfer medium to said compressor; compressing said second heat transfer medium using said compressor to supply said second heat transfer medium over said tube arrangement.

Optionally, the compressor is coupled to a shaft for driving the compressor.

Advantageously, this allows the compressor to be driven by an external power source such as an engine.

Optionally, the shaft is either mechanically driven by an engine or driven by an exhaust fluid of an engine.

Advantageously, this allows the compressor to be used in a supercharger or turbocharger arrangement, and increase the power output of the engine.

Optionally, said first heat transfer medium is a heatant and said second heat transfer medium is a coolant, or said first heat transfer medium is a coolant and said second heat transfer medium is a heatant. Advantageously, this increases the heat transfer coefficient of the method.

The first heat transfer medium may be water, or a mixture of water and ethylene glycol, or a mixture of water, ethylene glycol and at least one additional additive, or helium. The second heat transfer medium may be air or oxygen.

Optionally, said first heat transfer medium is supplied to said tube arrangement in a first direction and said second heat transfer medium is supplied to said compressor in a second direction, the flow arrangement of said first and second heat transfer mediums is substantially parallel flow or substantially counter flow.

Advantageously, the counter flow arrangement increases the effectiveness of the method.

Advantageously, the parallel flow arrangement may be used in applications where a lower effectiveness is required than the counter flow arrangement. This can have benefits such as reducing thermal stresses of the apparatus components.

According to a third aspect of the disclosure, there is provided a system comprising an engine and an integrated forced-induction and heat exchanger apparatus according to a first aspect of the disclosure and any optional feature thereon, wherein the outlet of the compressor is fluidly coupled to the air inlet of the engine.

By eliminating the need for a separate heat exchanger installation, the packaging of an engine may be improved due to the reduction in the number of components that must be fitted around said engine. In high performance automotive applications this is of significant benefit.

A pump may be provided to drive the first heat transfer medium through the heat exchanger apparatus.

The system may also include a radiator arrangement for removing heat from the system.

The system may further comprise a turbine and/or a shaft and/or a pump arrangement. Furthermore, the system may further comprise a cooler and/or a motor-generator unit and/or a storage unit. The heat exchanger arrangement of the apparatus may further comprise two or more sub-units. The pump arrangement may further comprise two or more pumps. The radiator arrangement may further comprise two or more sub-units.

The system may further comprise more than one first heat transfer medium loops. The system may use the first heat transfer medium to remove excess heat from features such as the engine or engine oil.

The system may further comprise a waste gate or inlet dump valve to control boost pressure and/or turbocharger speed. The system may further be configured to recirculate exhaust gas to control NOx formation and combustion temperatures of the engine.

The system may further comprise a motor-generator unit directly coupled to the turbine. This motorgenerator unit can be used to either capture excess kinetic energy from the turbine or increase the speed of the turbine when there is limited power available for extraction from the exhaust stream.

Optionally, the compressor is coupled to a shaft for driving the compressor.

Advantageously, this allows the compressor to be driven by an external power source such as an engine.

Optionally, the shaft is either mechanically driven by an engine or driven by an exhaust fluid of an engine.

According to a fourth aspect of the disclosure, there is provided a vehicle comprising an integrated forced-induction and heat exchanger apparatus according to a first aspect of the disclosure and any optional feature thereon. Such a vehicle may include, but is not limited to, wheeled vehicles including motorsport vehicles, marine vehicles, for example those with marine engines, and aerospace vehicles including those with aircraft fuel cells.

BRIEF SUMMARY OF THE DRAWINGS

The present disclosure will now be described by way of example with reference to the following drawings, in which:

Figure 1 is a perspective view of a first embodiment of an integrated forced-induction and heat exchanger apparatus;

Figure 2 is a front elevation of the integrated forced-induction and heat exchanger apparatus of Figure 1 ;

Figure 3 is a first partial cutaway perspective view of the integrated forced-induction and heat exchanger apparatus of Figure 1 ;

Figure 4 is a second partial cutaway perspective view of the integrated forced-induction and heat exchanger apparatus of Figure 1 ;

Figure 5 is a cross-sectional side elevation of the integrated forced-induction and heat exchanger apparatus of Figure 1 ;

Figure 6 is a cross-sectional front elevation of the integrated forced-induction and heat exchanger apparatus of Figure 1 ; Figure 7 is a partial cutaway perspective view of a second embodiment of an integrated forced-induction and heat exchanger apparatus;

Figure 8 is a cross-sectional side elevation of the integrated forced-induction and heat exchanger apparatus of Figure 7;

Figure 9 is a cross-sectional side elevation of a third embodiment of an integrated forced-induction and heat exchanger apparatus;

Figure 10 is a cross-sectional side elevation of a fourth embodiment of an integrated forced-induction and heat exchanger apparatus;

Figure 11 is a partial cutaway perspective view of the integrated forced-induction and heat exchanger apparatus of Figure 10;

Figure 12 is a schematic cycle diagram for a first system comprising an engine and the integrated forced-induction and heat exchanger apparatus of Figures 1 , 7, 9, or 10; and

Figure 13 is a schematic cycle diagram for a second system comprising an engine and the integrated forced-induction and heat exchanger apparatus of Figures 1 , 7, 9, or 10.

DETAILED DESCRIPTION

Figures 1 to 6 show a first embodiment of an integrated forced-induction and heat exchanger apparatus generally at 100. The integrated forced-induction and heat exchanger apparatus 100 comprises a heat exchanger arrangement 200 and a compressor 300.

The integrated forced-induction and heat exchanger apparatus 100 further comprises a central longitudinal axis 102, a first side 104, a second side 106, a first outer wall 108, a second outer wall 110, casing 112, and flow channels 1 14. The first and second sides 104, 106 are generally on opposing sides of the apparatus 100. The first outer wall 108 is arranged at the second side 106, and the second outer wall 110 is a lateral wall extending between the first and second sides of the apparatus 100.

The casing 112 comprises a first side and a second side corresponding with the first side 104 and the second side 106 of the apparatus 100, respectively. The second side of said casing having a larger cross-dimension than an equivalent cross-dimension of the first side of said casing. The casing 1 12 forms the walls of some of the flow channels 114 within the apparatus 100. In the present example, the first outer wall 108 and the second outer wall 1 10 are part of the casing 112, but in other examples may not be part of the casing 112.

The terms longitudinal and axial may be used interchangeably throughout this specification. Any radial direction is defined in relation to a longitudinal direction parallel with any longitudinal axis disclosed throughout this specification, for example the central longitudinal axis of the apparatus 100, 700, 900, 950. The heat exchanger arrangement 200 further comprises an axial aperture 202 therethrough, a plurality of tubes 204, an inner surface 210, and an outer surface 212. The plurality of tubes each have a first end and a second end.

The heat exchanger arrangement 200 is for carrying a first heat transfer medium, and is generally annular and tubular in form. In the example shown in Figures 1 to 6, the axial aperture 202 of the heat exchanger arrangement 200 shares the same central longitudinal axis as the apparatus 100, namely the central longitudinal axis 102. The rotational axis of the heat exchanger arrangement 200 is coincident with the central longitudinal axis 102 of the apparatus 100. In the present embodiment, the rotational axis of the compressor 300 is co-incident with the rotational axis of the heat exchanger arrangement 200, which is co-incident with the central longitudinal axis 102 of the apparatus 100.

The heat exchanger 200 is a shell and tube type heat exchanger. In Figures 4 and 6, the plurality of tubes 204 are shown schematically and are arranged generally as an involute spiral, each of the tubes following a spiral path. Figures 4 and 6 do not show each individual tube, however, and instead show simplified spiral blocks which may in reality be a plurality of substantially parallel tubes fluidly coupling a corresponding pair of inlet and outlet headers which are discussed in more detail below. In a preferred embodiment, each of the plurality of tubes have an outer cross-dimension of generally less than 1 millimetre. Examples of a plurality of tubes arranged as an involute spiral can be found in published patent documents GB2581840A and GB2519148A.

In the second embodiment discussed below, the plurality of tubes extend generally longitudinally, and at least one end plate is provided for fluidly coupling at least two of the plurality of tubes.

The compressor 300 is arranged at least partially within the axial aperture 202 of the heat exchanger arrangement 200. The heat exchanger arrangement 200 substantially overlaps the compressor 300. More specifically, with respect to the central longitudinal axis 102 of the apparatus 100, the heat exchanger arrangement 200 overlaps the compressor 300. The heat exchanger 200 also partially encloses the compressor 300, and the compressor 300 is arranged partially within the heat exchanger arrangement 200. The heat exchanger arrangement 300 can be seen as arranged, at least in part, axially before or in front of the compressor inlet with respect to the central longitudinal axis. The heat exchanger arrangement is though fluidly coupled downstream of the compressor. A portion of the compressor 300 is arranged outside of the axial aperture 202 of the heat exchanger arrangement 200.

The inner surface 210 of the heat exchanger arrangement 200 is a lateral inner surface of the heat exchanger arrangement 200, extending generally longitudinally. The inner surface 210 defines the axial aperture 202 of the heat exchanger arrangement 200. The outer surface 212 of the heat exchanger arrangement 200 is a lateral outer surface of the heat exchanger arrangement 200, extending generally longitudinally. The outer surface 212 of the heat exchanger arrangement 200 shares the same central longitudinal axis as the axial aperture 202 of the heat exchanger arrangement 200, namely the central longitudinal axis 102 of the apparatus 100. The compressor 300 further comprises a flow inlet 302, an impeller 308, an impeller housing 312, and a shaft 314. In the present example, the flow inlet 302, the impeller 308, and the impeller housing 312 are arranged substantially within the axial aperture 202 of the heat exchanger arrangement 200.

The flow inlet 302 further comprises a first portion 304 and a second portion 306. As can be seen in Figures 3 to 5, the first portion 304 is oriented generally radially, and the second portion 306 is oriented generally longitudinally. In other embodiments, the first portion 304 and the second portion 306 may be oriented in any direction. The first and second portions 304, 306 extend substantially perpendicularly to one another. The first and second portions 304, 306 are fluidly coupled and are configured for turning the second heat transfer medium from generally radial to generally longitudinally.

The compressor 300 shown in Figures 1 to 6 is a centrifugal compressor. The impeller 308 further comprises a plurality of blades 310, and is arranged substantially within the diffuser of the compressor 312. Each of the plurality of blades 310 is a semi-open full-blade, and includes backsweep. The impeller 308 is arranged substantially within the impeller housing 312.

The shaft 314 for driving the compressor 300, shown in Figures 3 and 5, is coupled to the compressor 300. More specifically, the shaft 314 is coupled to the impeller 308. The shaft 314 is either mechanically driven by an engine or driven by an exhaust fluid of an engine, allowing the compressor 300 to be used in a supercharger or turbocharger arrangement.

The integrated forced-induction and heat exchanger apparatus 100 further comprises an inlet manifold 116, an outlet manifold 118, at least one inlet header 120, and at least one outlet header 122.

The inlet manifold 116 is generally annular in form, and is fluidly coupled to the heat exchanger arrangement 200 for delivering the first heat transfer medium thereto. In the embodiment shown, the inlet manifold 1 16 is formed as one continuous chamber and is arranged at a first side 104 of the apparatus 100. The inlet manifold 116 further comprises an inlet manifold inlet 117. The inlet manifold inlet 117 extends generally longitudinally.

The inlet manifold 116 is coupled to the heat exchanger arrangement 200 via the at least one inlet header 120. In the embodiment shown, there are more than two inlet headers 120, more specifically ten. In some embodiments not shown, there may be just one inlet header 120. The at least one inlet header 120 is coupled to a first end of at least one of the plurality of tubes 204, and extends generally longitudinally.

The outlet manifold 118 is generally annular in form, and is fluidly coupled to the heat exchanger arrangement 200 for receiving the first heat transfer medium therefrom. In the embodiment shown, the outlet manifold 118 is formed as one continuous chamber and is arranged at a first side 104 of the apparatus 100. The outlet manifold 118 further comprises an outlet manifold outlet 1 19. The outlet manifold outlet 119 extends generally longitudinally. The outlet manifold 1 18 is coupled to the heat exchanger arrangement 200 via the at least one outlet header 122. In the embodiment shown, there are more than two outlet headers 122. In some embodiments not shown, there may be just one outlet header 122. The at least one outlet header 122 is coupled to a second end of at least one of the plurality of tubes 204, and extends generally longitudinally.

The inlet and outlet manifolds 116, 118 are arranged on a common side of the apparatus, namely the first side 104, are generally aligned, are generally concentric, and share the same central longitudinal axis 102 as the axial aperture 202 of the heat exchanger arrangement 200. The inlet and outlet manifolds 116, 118 are formed as one integral part.

The integrated forced-induction and heat exchanger apparatus 100 further comprises a flow outlet 124, a first turning flow channel 126, and a second turning flow channel 138.

The flow outlet 124 is a circumferential radially extending flow outlet from the compressor 300. The flow outlet 124 is aligned with an exit of the compressor, and in the present example comprises one continuous volume. More specifically, the flow outlet 124 is aligned with an exit of the impeller housing 312 of the compressor 300. The flow outlet 124 is arranged adjacent a second side 106 of the apparatus 100. More specifically, the flow outlet 124 is arranged adjacent the first outer wall 108 of the apparatus 100 which is arranged at the second side 106 of the apparatus 100. The flow outlet 124 is disc-shaped and annular in form.

The first turning flow channel 126, where flow may be turned from generally radial to generally longitudinal and back to generally radial across the heat exchanger arrangement 200, is arranged adjacent the outer surface 212 of the heat exchanger arrangement 200, and is coupled to the flow outlet 124. The first turning flow channel 126 is arranged substantially between the outer surface 212 and the second outer wall 110 of the apparatus 100. The second outer wall 110 extends in a direction with both radial and longitudinal components, and is coupled to the first outer wall 108. As seen in Figure 5, the first turning flow channel 126 has a first cross-dimension 128 taken in a radial plane at the first side 104 of the apparatus 100, and a second cross-dimension 130 taken in a radial plane at the second side 106 of the apparatus 100. The second cross-dimension 130 is larger than the first cross-dimension 128. The first turning flow channel 126 is adjacent at least one inlet header 120 and/or at least one outlet header 122.

The integrated forced-induction and heat exchanger apparatus 100 further comprises an inlet turning vane 132. The inlet turning vane 132 includes a leading edge 134 and a trailing edge 136. The inlet turning vane 132 is arranged substantially within the first turning flow channel 126. The inlet turning vane 132 has an arcuate profile, extends circumferentially, and is an annular and substantially circular ring. In the present example, there is one inlet turning vane. The inlet turning vane 132 has a substantially constant thickness between the leading edge 134 and the trailing edge 136, other than any streamlining curvature at either edge 134, 136. In the present example, the second heat transfer medium flows in a generally radially inward, towards the central longitudinal axis 102, across the heat exchanger arrangement 200.

The second turning flow channel 138, where flow from across the heat exchanger arrangement 200 is turned from generally radial to generally longitudinal, is arranged adjacent the inner surface 210 of the heat exchanger arrangement 200, and is coupled to the first turning flow channel 126. The second turning flow channel 138 is arranged substantially between the inner surface 210 and the compressor 300. The second turning flow channel 138 is generally annular in form.

The integrated forced-induction and heat exchanger apparatus 100 further comprises two exit turning vanes 140. Each exit turning vane 140 comprises a leading edge 142 and a trailing edge 144. The exit turning vanes 140 are arranged substantially within the second turning flow channel 138. Each exit turning vane 140 has an arcuate profile, extends circumferentially, and is an annular and substantially circular ring. Each exit turning vane 140 has a substantially constant thickness between the leading edge 142 and the trailing edge 144, other than any streamlining curvature at either edge 134, 136. Common parts of the exit turning vanes are arranged at different distances from the heat exchanger arrangement 200. In the present example, the trailing edges 144 are arranged different distances from the heat exchanger arrangement 200. The exit turning vanes 140 are concentric about the central longitudinal axis of the axial aperture 202 of the heat exchanger arrangement 200 which is coincident with the central longitudinal axis 102 of the apparatus 100. The exit vanes 140 are internested with one another.

The integrated forced-induction and heat exchanger apparatus 100 further comprises an air exit volute 146. The air exit volute 146 is arranged at the first side 104 of the apparatus 100, and is further arranged substantially around the compressor 300. The air exit volute 146 is coupled to the second turning flow channel 138 and is generally annular in form. The air exit volute further comprises an air exit volute housing 148. The air exit volute is bounded by the air exit volute housing 148 and the compressor 300. In the present example, one of the air exit turning vanes 140 is arranged at least partially within the air exit volute 146.

In the present embodiment, the heat exchanger arrangement 200, compressor 300, and casing 112 of the apparatus 100 are each made from an aluminium alloy although other materials, including metal alloys are also envisaged depending on application. The apparatus may include parts which are manufactured using a 3D printing process.

In an example operation, the first heat transfer medium enters the heat exchanger arrangement 200 of the apparatus 100 through the inlet manifold inlet 117 before travelling through the inlet manifold 116 to the inlet headers 120. The inlet headers 120 distribute the first heat transfer medium to the plurality of tubes 204. Whilst in the plurality of tubes 204, the first heat transfer medium receives thermal energy from the second heat transfer medium flowing over the plurality of tubes 204, cooling the second heat transfer medium. The first heat transfer medium then flows out of the plurality of tubes 204 to the outlet headers 122. From the outlet headers 122, the first heat transfer medium then enters the outlet manifold 118 before leaving the heat exchanger arrangement 200 though the outlet manifold outlet 1 19.

In the same example operation, the second heat transfer medium flows though the flow inlet 302 of the compressor, before entering the impeller housing 312. Here, the impeller 308 compresses the second heat transfer medium which travels generally radially outwards through the flow outlet 124 before being turned generally radially inward in the first turning flow channel 126. The second heat transfer medium then passes over the heat exchanger arrangement 200 where it transfers thermal energy to the first heat transfer medium flowing within the plurality of tubes 204 of the heat exchanger arrangement 200. The second heat transfer medium then enters the second turning flow channel 138 within the axial aperture 202 where the second heat transfer medium is turned generally longitudinally. The second heat transfer medium then enters the air exit volute 146 before leaving the apparatus 100.

Figure 7 is a partial cutaway perspective view of a second embodiment of an integrated forced-induction and heat exchanger apparatus 700. The first and second embodiments of apparatus 100, 700 are substantially the same, aside from the second embodiment 700 comprises an alternate heat exchanger arrangement 800 compared with the heat exchanger arrangement 200 of the first embodiment. In the heat exchanger apparatus 800, a plurality of tubes 804 extend generally longitudinally, with respect to the central longitudinal axis of the apparatus 700, and at least one end plate 806 is provided for fluidly coupling at least two of a plurality of tubes.

Similar to the first embodiment of the integrated forced-induction and heat exchanger apparatus 100, the integrated forced-induction and heat exchanger apparatus 700 further comprises an inlet manifold 716, an outlet manifold 718.

The inlet manifold 716 is generally annular in form, and is fluidly coupled to the heat exchanger arrangement 800 for delivering the first heat transfer medium thereto. In the embodiment shown, the inlet manifold 716 is formed as one continuous chamber and is arranged at a first side 704 of the apparatus 700. The inlet manifold 716 further comprises an inlet manifold inlet 717. The inlet manifold inlet 717 extends generally longitudinally.

The outlet manifold 718 is generally annular in form, and is fluidly coupled to the heat exchanger arrangement 800 for receiving the first heat transfer medium therefrom. In the embodiment shown, the outlet manifold 718 is formed as one continuous chamber and is arranged at a first side 704 of the apparatus 700. The outlet manifold 718 further comprises an outlet manifold outlet 719. The outlet manifold outlet 719 extends generally longitudinally.

In the example shown, there are three end plates 830, 832, 834. Each end plate 830, 832, 834 defines a turning volume for turning a flow of the first heat transfer medium. Each end plate 830, 832, 834 is generally annular in form, and in the embodiment shown each defines one continuous turning volume. The second end plate 832 is arranged at a first side 704 of the apparatus 700, and the first and third end plates 830, 834 are arranged closer to a second side 706 of the apparatus than the first side 704. Further, in the example shown, the first end plate 830 and the third end plate 834 are formed as one integral part.

The inlet and outlet manifolds 716, 718 and the second end plate 832 are all arranged on a common side of the apparatus, namely the first side 704, are generally aligned, are generally concentric, and share the same central longitudinal axis 702 as the axial aperture 802 of the heat exchanger arrangement 800. The second end plate 832 is arranged between the inlet and outlet manifolds 716, 718. In the example shown, the inlet manifold 716, the outlet manifold 718, and the second end plate 832 are formed as one integral part.

At least one of the plurality of tubes 804 may be coupled directly to the inlet and/or outlet manifolds 716, 718. In Figures 7 and 8, the plurality of tubes 804 are shown schematically and are arranged such that they extend generally longitudinally. Figures 7 and 8 do not show each individual tube, however, and instead show simplified longitudinally-extending blocks which may in reality be a plurality of substantially parallel tubes. In a preferred embodiment, each of the plurality of tubes have an outer cross-dimension of generally less than 1 millimetre. In the example shown, there are four tube blocks 820, 822, 824, 826. The first tube block 820 is fluidly coupled at a first end to an inlet manifold 716 and at a second end to the first end plate 830. The second tube block 822 is fluidly coupled at a first end to the first end plate 830, and at a second end to the second end plate 832. The third tube block 824 is fluidly coupled at a first end to the second end plate 832, and at a second end to the third end plate 834. The fourth tube block is fluidly coupled at a first end to the third end plate 834, and at a second end to an outlet manifold 718.

In an example operation, the first heat transfer medium enters the heat exchanger arrangement 800 of the apparatus 700 through the inlet manifold inlet 717 before travelling through the inlet manifold 716. The inlet manifold 716 directly distributes the first heat transfer medium to the first tube block 820 of the plurality of tubes 804. Whilst in the plurality of tubes 804, the first heat transfer medium receives thermal energy from the second heat transfer medium flowing over the plurality of tubes 804, cooling the second heat transfer medium. The first heat transfer medium then flows through and out of the first tube block 820 into a turning volume defined by the first end plate 830. In the turning volume of the first end plate 830, the flow of the first heat transfer medium is turned from longitudinal to radial and back to longitudinal, substantially 180 degrees, before entering the second tube block 822. The first heat transfer medium then flows through and out of the second tube block 822 into the turning volume defined by the second end plate 832. Here, the flow of the first heat transfer medium is turned from longitudinal to radial and back to longitudinal, substantially 180 degrees, before entering the third tube block 824. The first heat transfer medium then flows through and out of the third tube block 824 into the turning volume defined by the third end plate 834. Here, the flow of the first heat transfer medium is turned from longitudinal to radial and back to longitudinal, substantially 180 degrees, before entering the fourth tube block 826. The first heat transfer medium then flows though and out of the fourth tube block 826 directly to the outlet manifold 718 before leaving the heat exchanger arrangement 800 though the outlet manifold outlet 719. A third embodiment of an integrated forced-induction and heat exchanger apparatus 900, shown in Figure 9, is substantially the same as the first and second embodiments 100, 700, aside from the third embodiment 900 further comprising an additional compressor in what may be known as a ‘back-to-back’ compressor arrangement. In the third embodiment 900, the compressor arrangement 910 comprises a first compressor 912 with a first flow inlet 914 and a first impeller 916, and a second compressor 918 with a second flow inlet 920 and a second impeller 922.

The compressor arrangement 910 further comprises an impeller housing 923 and a shaft 924. The first and second impellers, 916, 922, are both arranged within the impeller housing 923. The shaft 924 is coupled to the first and second compressor arrangements to drive said compressors 912, 918. More specifically, the shaft 924 is coupled to the first and second impellers 916, 922, and is substantially aligned with a central longitudinal axis 902 of the apparatus 900.

In the embodiment shown, the first compressor 912 is arranged substantially within an axial aperture 906 of a heat exchanger arrangement 904, similarly to the heat exchanger arrangement 200 and axial aperture 202 of the first apparatus embodiment 100. Further, the first flow inlet 914 is arranged in a first direction, and the second flow inlet 920 is arranged in a second opposing direction. In this third embodiment, the first and second flow inlets 914, 920 are aligned with the central longitudinal axis 902.

In an example operation, the second heat transfer medium flows through the flow inlets 914, 920 of the compressors 912, 918, in first and second directions, respectively, before entering the impeller housing 923. The first compressor is arranged such that the second heat transfer medium entering the impeller housing 923 from the first flow inlet 914 is compressed by the first impeller 916 and travels radially outwards through the flow outlet 926, similarly to the flow outlet 124 of the apparatus 100. The second compressor is arranged such that the second heat transfer medium entering the impeller housing from the second flow inlet 920 is compressed by the second impeller 922 and also travels radially outwards through the flow outlet 926, mixing with the second heat transfer medium compressed by the first impeller.

A fourth embodiment of an integrated forced-induction and heat exchanger apparatus 950, shown in Figures 10 and 11 , is substantially the same as the first and second embodiments 100, 700, aside from the fourth embodiment 950 comprising a heat exchanger arrangement 960, analogous to the heat exchanger arrangement 200 of the apparatus 100, in two stages: a first heat exchanger stage 962, and a second heat exchanger stage 972. Each of the first and second stages 962, 972 are comparable to the heat exchanger arrangement 200 of the apparatus 100, further comprising inlet and outlet manifolds and headers for fluidly coupling said stages 962, 972.

The first stage 962 comprises a first inlet manifold 964, a first outlet manifold 966, first inlet headers 968, first outlet headers 970, and a first plurality of tubes 971 . These features are analogous to inlet manifold 116, outlet manifold 1 18, inlet headers 120, outlet headers 122, and plurality of tubes 204 of the apparatus 100.

The second stage 972 comprises a second inlet manifold 974, a second outlet manifold 976, second inlet headers 978, second outlet headers 980, and a second plurality of tubes 981 . Again, these features are analogous to inlet manifold 116, outlet manifold 1 18, inlet headers 120, outlet headers 122, and plurality of tubes 204 of the apparatus 100.

In Figures 10 and 11 and 6, the pluralities of tubes 971 , 981 are shown schematically and are arranged generally as an involute spiral, each of the tubes following a spiral path. Figures 10 and 11 do not show each individual tube, however, but instead show simplified spiral blocks representative of a plurality of substantially parallel tubes. In other embodiments, one or more of the pluralities of tubes 971 , 981 may extend generally longitudinally, with at least one end plate provided for fluidly coupling at least two of said tubes.

In the embodiment shown, the two stages 962, 972 are arranged about a central longitudinal axis 952 of the apparatus 950. The first and second stages 962, 972, each have an axial aperture defined therethrough, and share the same central longitudinal axis 952 as the apparatus 950. The second stage 972 is arranged at least partially within the axial aperture of the first stage 962.

The first inlet and first outlet manifolds 964, 966 and the second inlet and outlet manifolds 974, 976 are arranged on a common side of the apparatus, are generally aligned, are generally concentric, and share the same central longitudinal axis 952 as the axial apertures defined through the first and second stages 962, 972.

In an example operation, in the heat exchanger arrangement 950 the first and second inlet manifolds 964, 974 are supplied with a first heat transfer medium, the respective first heat transfer medium may be from different circuits, before traveling through said inlet manifolds 974, 974 to the first and second inlet headers 968, 978, respectively. It is also possible that each of the first and second inlet manifolds 964, 974 is supplied with a different heat transfer medium. The inlet headers 968, 978 distribute the heat transfer medium to the first and second plurality of tubes 971 , 981 , respectively. Whilst in the pluralities of tubes 971 , 981 , the first heat transfer medium receives thermal energy from the second heat transfer medium flowing over said tubes 971 , 981 , cooling the second heat transfer medium. The second heat transfer medium flows over the first plurality of tubes 971 before flowing over the second plurality of tubes 981 . The first heat transfer medium then flows out of the pluralities of tubes 971 , 981 , to the first and second outlet headers, 970, 980. From the outlet headers 970, 980, the first heat transfer medium then enters the first and second outlet manifolds 966, 976, respectively, before leaving the heat exchanger arrangement 960.

Figure 12 shows a schematic view of the cycle for a first system 600 comprising an engine and the integrated forced-induction and heat exchanger apparatus 500. The apparatus 500 may be an installed version of the apparatus embodiments 100, 700, 900, 950 described above, and may comprise the same features.

The first system 600 comprises an integrated forced-induction and heat exchanger apparatus 500, an engine 510, a turbine 512, a shaft 514, a pump arrangement 516, a radiator arrangement 522, a first heat transfer medium circuit 400, and a second heat transfer medium flow stream 420. The apparatus 100 comprises a heat exchanger arrangement 502, and a compressor arrangement 508.

The first heat transfer medium circuit comprises a plurality of streams 402, 404, 406 of the first heat transfer medium. The second heat transfer medium flow stream 420 comprises a plurality of streams 424, 426, 428, 430, 432, 434, 436 of the second heat transfer medium.

The compressor arrangement 508 is coupled to a turbine 512 via a shaft 514. A first ambient low pressure stream 432 of the second heat transfer medium 420 enters the compressor arrangement 508. The compressor arrangement 508 compresses this stream 422 into a hot high pressure stream 424. The hot high pressure stream 424 passes over the heat exchanger arrangement 502 which cools said stream 424, and stream 424 becomes warm high pressure stream 426. The warm high pressure stream 426 travels to the engine 510 where it is combusted with fuel. This combustion heats the stream 425 and it becomes hot high pressure exhaust stream 428. This exhaust stream 428 travels to the turbine 512, and drives said turbine 512. This process converts the exhaust stream 428 to a warm low pressure exhaust stream 430.

At the heat exchanger arrangement 502, the hot high pressure stream 424 of the second heat transfer medium 420 is cooled by an ambient high pressure coolant stream 402 of the first heat transfer medium 400. This cooling of the hot high pressure stream 424 heats the ambient high pressure coolant stream 402 to become hot high pressure coolant stream 404. The hot high pressure coolant stream 404 then travels to the radiator arrangement 522 which extracts thermal energy from the coolant stream 404. As a result of this extraction, the coolant stream 404 becomes ambient low pressure coolant stream 406. A second ambient low pressure stream 434 of the second heat transfer medium 420 enters the radiator arrangement 522 where it is heated by the energy from the hot high pressure coolant stream 404 becoming warm low pressure reject stream 436. This stream 436 then leaves the system. The ambient low pressure coolant stream 406 enters the pump arrangement 516 which provides the energy to circulate the first heat transfer medium through the system 600.

A second system 602 is shown in Figure 13. Again, the apparatus 500 may be an installed version of the apparatus embodiments 100, 700, 900, 950 described above, and may comprise the same features.

The second system 602 comprises the same features as the first system 600 designated with the same reference numerals, discussed above, aside from those discussed below.

In the second system 602, the heat exchanger arrangement 502 further includes a first heat exchanger sub-unit 504 and a second heat exchanger sub-unit 506. The pump arrangement 516 further comprises a first pump 518 and a second pump 520. Furthermore, the radiator arrangement 522 further comprises a first radiator sub-unit 524 and a second radiator sub-unit 526. The second system 602 further comprises a cooler 528, motor-generator unit 530, and storage unit 532.

As seen in Figure 13, a motor-generator unit 530 is mechanically coupled to the same shaft 514 coupling the engine 510 and the turbine 512. The motor-generator unit 530 is electrically coupled to the storage unit 532. The motor-generator unit 530 can act either as a motor or a generator depending on whether it is deemed preferable to capture excess kinetic energy from the turbine 512 or increase the speed of the turbine 512, for example when there is limited power available for extraction from the hot high pressure exhaust stream 428.

In the second system 602, the first heat transfer medium circuit 400 is split into two fluidly separate sections 407, 413, each comprising a plurality of streams 408, 410, 412, 414, 415, 416, 418. This enables the first heat transfer medium circuit to meet the overall cooling demands of the system whilst avoiding undesirable effects of cooling such as boiling of the first heat transfer medium 400 when the first heat transfer medium 400 is a liquid.

The first heat transfer medium within the first section 407 is pumped by the first pump 518, heated by the first heat exchanger sub-unit 504, and cooled by the first radiator sub-unit 524. A first ambient high pressure coolant stream 408 leaves the first pump 518 where it passes through the engine 510 to cool said engine 510. This heats the coolant stream 408 to become first warm high pressure coolant stream 409. This stream 409 then travels to the first heat exchanger sub-unit 504 where it is heated to become first hot high pressure coolant stream 410. This coolant stream 410 then travels to the first radiator subunit 524 which cools said coolant stream 410 to become first ambient low pressure coolant stream 412. This coolant stream 412 then travels to the first pump 518, and the cycle begins again.

The first heat transfer medium within the second section 413 is pumped by the second pump 520, heated by the cooler 528, further heated by the second heat exchanger sub-unit 504, and cooled by the second radiator sub-unit 526. A second ambient high pressure coolant stream 414 leaves the second pump 520. The stream 414 then passes through the cooler 528. The cooler 528 may cool the engine 510 directly, or may cool another feature, for example engine oil. This heats the coolant stream 414 to become second warm high pressure coolant stream 415. This stream 415 then travels to the second heat exchanger sub-unit 506 where it is heated to become second hot high pressure coolant stream 416. This coolant stream 416 then travels to the second radiator sub-unit 526 which cools said coolant stream 416 to become second ambient low pressure coolant stream 418. This coolant stream 418 then travels to the second pump 520, and the cycle begins again.

The hot high pressure stream 424 of the second heat transfer medium flow stream 420 passes through the first heat exchanger sub-unit 504 before passing through the second heat exchanger sub-unit 506. As a result of passing through the heat exchanger sub-units, the stream 424 becomes warm high pressure stream 426. The second ambient low pressure stream 434 of the second heat transfer medium flow stream 420 splits and passes through the first and second radiator sub-units 524, 526 in parallel before being exhausted as warm low pressure reject stream 436.