EP3246647B1 - Dispositif d'échange de chaleur - Google Patents

Dispositif d'échange de chaleur Download PDF

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Publication number
EP3246647B1
EP3246647B1 EP16382220.8A EP16382220A EP3246647B1 EP 3246647 B1 EP3246647 B1 EP 3246647B1 EP 16382220 A EP16382220 A EP 16382220A EP 3246647 B1 EP3246647 B1 EP 3246647B1
Authority
EP
European Patent Office
Prior art keywords
manifold
fluid
shell
heat exchanger
inlet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16382220.8A
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German (de)
English (en)
Other versions
EP3246647A1 (fr
Inventor
Manuel José DIÉGUEZ FORTES
Simón Piñeiro Losada
Julio Abraham CARRERA GARCÍA
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BorgWarner Emissions Systems Spain SL
Original Assignee
BorgWarner Emissions Systems Spain SL
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by BorgWarner Emissions Systems Spain SL filed Critical BorgWarner Emissions Systems Spain SL
Priority to EP16382220.8A priority Critical patent/EP3246647B1/fr
Priority to US15/596,646 priority patent/US20170336147A1/en
Priority to CN201710352163.XA priority patent/CN107401939A/zh
Publication of EP3246647A1 publication Critical patent/EP3246647A1/fr
Application granted granted Critical
Publication of EP3246647B1 publication Critical patent/EP3246647B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F28D7/0083—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with units having particular arrangement relative to a supplementary heat exchange medium, e.g. with interleaved units or with adjacent units arranged in common flow of supplementary heat exchange medium
    • F28D7/0091—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with units having particular arrangement relative to a supplementary heat exchange medium, e.g. with interleaved units or with adjacent units arranged in common flow of supplementary heat exchange medium the supplementary medium flowing in series through the units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/28—Layout, e.g. schematics with liquid-cooled heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0026—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for combustion engines, e.g. for gas turbines or for Stirling engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core

Definitions

  • the present invention is a heat exchange device characterized by a particular configuration of the liquid inlet or outlet manifold wherein a baffle formed from the shell itself is incorporated.
  • This configuration allows not only suitably orienting the inflow in regions of the tube bundle of the exchanger where convection must be more intense, but also allows generating a flow suitable for reaching all the regions having a higher convective heat transfer requirement.
  • Configuring a baffle from the shell prevents incorporating and manufacturing specific additional parts as well as the additional operations required for their configuration and attachment to the heat exchanger.
  • the present invention is useful in the application of environmental protection measures.
  • the heat exchange is carried out in a tube bundle in which the configuration of the tubes can be very diverse, for example they can be corrugated tubes, flat tubes or tubes configured by stacking die-cut and stamped plates.
  • a hot gas from the combustion chambers of the internal combustion engine circulates inside the tubes, and a liquid suitable for removing the heat from the gas circulates on the outside of said tubes.
  • the liquid is either a liquid coolant or else a liquid intended for changing phase, for example, to be part of a thermodynamic cycle that allows obtaining mechanical energy from the thermal energy extracted from the gas.
  • first fluid the fluid circulating inside the tube bundle
  • second fluid the fluid circulating in the space defined between the inner wall of the shell and the outside of the tubes of the tube bundle
  • each tube of the tube bundle will vary along the length thereof since the first fluid, the hot fluid circulating on the inside, interchanges heat through the wall of the tube with the fluid flowing on the outside. Therefore, the end of the tube where the hot fluid enters is the end where the temperature is the highest.
  • This temperature distribution is not the same for all the tubes of the tube bundle.
  • the fluid with which heat is exchanged flows from an inlet into the shell of the exchanger to an outlet from same, and although all the points of the inside of the shell of the heat exchanger are fluidically communicated with the inlet and outlet, the flow line passing through said point is different. There are preferred paths offering less resistance, favoring greater flow of liquid. There are also somewhat inaccessible regions, such as corners, wherein the flow velocity is lower, and therefore the heat exchange with the tubes is reduced due to less convection.
  • the second fluid It is generally necessary for the second fluid to have the highest possible velocity in a region determined as a section that is transverse to the bundle and located as close as possible to the inlet for the first fluid, the hot gas.
  • An alternative way to divert the jet inlet flow is to include additional parts inside the conduit through which the liquid enters the shell. These parts redirect part of the liquid jet, which is always at a high velocity, towards those regions of the heat exchanger which, were this baffle not included, would have a lower velocity. This is the case of the solution described in patent document WO 2015121148A1 .
  • baffles are formed by partial closures of the conduit through which the liquid accesses the shell of the heat exchanger, and comprising perforations generating jets having a higher velocity oriented in a specific direction. Although these jets acquire a higher velocity, they do not have a uniform configuration that can cover the entire inlet section adjacent to the end of the tube bundle where the hot gas enters and cause substantial pressure drops.
  • the present invention solves these problems without the addition of specific parts, but rather establishes a configuration combining an extension of the shell into the liquid inlet/outlet manifold and a slot.
  • This combination modifies the entry path of the second fluid due to a deflection effect, giving rise to a laminar flow, without important throttling causing pressure drops, throughout a section and with a modulated flow rate at each point of the section according to the application.
  • Heat exchangers according to the preamble of claim 1 are disclosed in patent documents JP 2009 114923 A , WO 2013/022072 A1 and JP 2009 091948 A .
  • the present invention is a heat exchanger for the heat exchange between a first fluid, which can be a hot gas, for example, and a second fluid, which can be a liquid, for example.
  • a first fluid which can be a hot gas, for example
  • a second fluid which can be a liquid, for example.
  • the preferred application of this invention is a heat exchanger for EGR systems, it also can be applied in other heat exchangers, such as evaporators or condensers.
  • the heat exchanger according to the invention comprises:
  • the tube bundle drives the first fluid, for example hot gas, from one end to the other end, allowing the heat exchange along the length thereof with the second fluid in which the tube bundle is immersed.
  • first fluid for example hot gas
  • the tube bundle is housed in a shell establishing a space between its inner wall and the outside of the tubes of the tube bundle where the second fluid, a liquid, for example, circulates.
  • This inner space is closed by the shell on the sides of the tube bundle.
  • the closure of the inner space at the ends of the tube bundle can be done in several ways.
  • the closure is established for a tube bundle of flat tubes by means of the use of baffles.
  • the closure is established for a tube bundle, wherein the tubes are formed by stacked plates, by means of a configuration of the tubes in the tube bundle in which the ends of the tubes are expanded. On the stacking of the tubes, such tubes are supported on one another in the expanded area and leave in the intermediate area passage channels for the second fluid with which the transfer of heat is established.
  • This second configuration prevents using baffles and maximizes the area for entry into the tubes of the tube bundle.
  • the inlet for the first fluid is formed by the set of openings of the tube bundle which allow the entry of hot gas
  • the outlet for the first fluid is formed by the set of openings of the tube bundle which allow the exit of said hot gas.
  • the second fluid entering the shell accesses the inside of same through a tubular inlet segment and exits through a tubular outlet segment.
  • tubular segments can be, for example, connecting segments (or spigots) with flexible conduits, or they can be the end portion of a conduit reaching the heat exchanger configured for driving the liquid with which heat is exchanged.
  • the present invention additionally verifies that:
  • the inlet/outlet for the second fluid in the heat exchanger according to the invention is established by means of a manifold, the one identified as first manifold, located between the shell and the tubular segment which drives the liquid of or from the inlet/outlet.
  • the flow velocity in the tubular segment where the second fluid enters is high given that the passage section is much smaller than the section of the space formed between the inner wall of the shell and the tube bundle.
  • the manifold allows generating a chamber or inner space that adapts the diameter of the tubular segment to a section having larger dimensions.
  • the manifolds allow the access of the second inlet fluid to a much larger region for entry into the shell, the one established by the support base of the manifold in the shell.
  • This expansion of the manifold does not allow good distribution of the flow because an adverse pressure gradient generates an unstable flow, with recirculation zones, and therefore is not capable of being suitably distributed reaching stagnation regions inside the shell.
  • the opening in the shell through which the second fluid passes does not coincide with the base of the manifold.
  • the opening is a slot having smaller dimensions than the base of the manifold and additionally comprising an extension of the shell into the manifold.
  • the extension of the shell into the manifold covers the restricted area of the base of the manifold not corresponding to the slot.
  • the slot has a longitudinal configuration and is oriented transverse to the tube bundle to allow generating a laminar flow in which a cross section of the tube bundle is immersed.
  • the slot has a variable width along its length depending on the flow rate to be introduced through each point of its length, which allows modulating the flow rate at different points of the section of the tube bundle.
  • the inlet for the second fluid meets with an expansion due to the first manifold. Nevertheless, the presence of the slot generates a reduction in the section increasing the flow velocity according to a configuration in the form of a laminar flow which prevents the existence of stagnation regions in entire regions of a section of the tube bundle, the cross section determined by the position of the slot according to the longitudinal direction.
  • the laminar flow allows increasing the convective heat transfer at all the points of the tube bundle where the temperature is higher, reducing thermal fatigue and increasing the service life of the device.
  • This restriction of the passage formed by the slot is obtained from an extension of the shell, preventing the need to make specific parts that must be attached to the inside of the manifold.
  • a particular embodiment of the invention wherein the extension of the shell is at least partially interposed in the path established by the geometric extension of the tubular segment attached to the first manifold is also of enormous interest.
  • the inflow tends to follow the path established by the geometric extension of the tubular segment due to inertia.
  • This inertia makes the inflow through the tubular segment be non-homogenous when it passes through the manifold and maintain the jet effect without distributing the velocity field along the base of the first manifold and particularly along the slot.
  • the jet inlet flow is deflected so that the outlet velocity of the second fluid through the slot is more homogenous although said slot is wide without having big pressure drops.
  • the present invention is a heat exchange device for the transfer of a first fluid to a second fluid.
  • the heat exchanger is a heat exchanger for an EGR system where the first fluid (11) is a hot gas and the second fluid (12) is a liquid coolant.
  • Figure 1 shows a heat exchange device formed by a main body comprising a shell (6) housing a tube bundle (5), which can be clearly seen in the sections shown in Figures 3 and 5 , for heat exchange.
  • the main body has a prismatic configuration with rectangular bases and extends along a longitudinal direction identified as X-X', as shown in the sections of Figures 3 and 5 .
  • the tube bundle (5) is formed by flat tubes fixed at their ends to a first baffle (1) and to a second baffle (2). As shown in Figure 5 , the inlet (I) for the first fluid is at the access openings into the inside of the flat tubes of the tube bundle (5), and the outlet (0) for the first fluid is at the access openings at the opposite end, wherein in this embodiment the ends of the flat tubes slightly overtakes the surface of the first baffle (1) and of the second baffle (2).
  • the shell (6) in this embodiment is made of die-cut and stamped plate configured with reinforcement ribs (6.3).
  • the first baffle (1) and the second baffle (2) are prolonged, perimetrally encircling the ends of the shell (6), according to the longitudinal direction X-X', establishing the closure of the inside of the shell (6) at respective ends.
  • the inlet and outlet (I, 0) for the first fluid is guided by means of second manifolds (9, 10), the main body of which is also made of die-cut and stamped plate.
  • the attachment of both second manifolds (9, 10) to the main body of the heat exchanger is established by means of a seating of the second manifold (9, 10) perimetrally embracing its corresponding baffle (1, 2).
  • Two tubular segments are shown on the shell (6), a first tubular inlet segment (7) and a second tubular outlet segment (8) for the entry and exit of the second fluid (12), respectively.
  • the first tubular inlet segment (7) is attached to a first manifold (3), obtained in this embodiment from die-cut and stamped plate, which in turn is attached to the outside of the shell (6) through a base (3.1) configured in the form of a perimetral strip.
  • the second tubular outlet segment (8) is attached to the shell (6), without the participation of a manifold, by means of a flaring or conical transition of the same shell (6).
  • the lack of space in the engine compartment determines that the positions and orientations of the conduits of the first fluid (11) and of the second fluid (12) cannot be optimal and are determined by the position of other components which are also housed in the same engine compartment.
  • the inlet for second fluid (12) is located at the end corresponding to the inlet (I) for the first fluid on one side of the upper rectangular surface of the shell (6) and with an oblique access; and the outlet for the second fluid (12) is located in a diagonally opposite position on the same upper rectangular surface of the shell (6), at the end corresponding to the outlet (0) for the first fluid.
  • the first manifold (3) has a base (3.1) having a configuration that is elongated and rounded at the ends which sits on the outer surface of the shell (6).
  • the shell (6) has reinforcement ribs, in this support zone of the first manifold (3) the configuration is flat to make the also flat seating of the base (3.1) of the first manifold (3) easier.
  • the shell (6) has an opening in the form of slot (6.2) spaced from the inlet (I) for the first fluid to allow the base (3.1) of the manifold to surround the slot (6.2), which is elongated and arranged transverse to the tube bundle (5) extending according to the longitudinal direction X-X'.
  • the width of the slot (6.2) is decreasing, having a greater width at the end near the inlet for the second fluid (12) and a smaller width at the opposite end.
  • the zone having a smaller width increases the velocity of the second fluid (12) going through said slot (6.2), favoring said second fluid (12), the liquid coolant, from going through the tube bundle (5) in this section near the inlet (I) for the first fluid, hot gas.
  • the width of the slot (6.2) allows regulating the velocity and the passage section of the second fluid (12) regardless of the shape of the seating of the first manifold (3).
  • Figure 4 allows observing that the shell (6) is extended internally according to an extension (6.1) which is what interferes with the flow passing through the inner chamber formed by the first manifold (3).
  • This extension (6.1) allows modifying the path of the flow before going through the slot (6.2) generating a more homogenous outflow of the second fluid (12) .
  • FIGS 6 to 10 show a second embodiment not within the scope of the invention, a condenser for recovering heat from a fluid in the gas phase.
  • This condenser is a heat exchanger that transfers heat from the first fluid (11), a fluid in vapor phase such as ethanol, for example, to the second fluid (12), a liquid, for the purpose of bringing about the change of phase in the first fluid (11).
  • the heat exchanger is configured according to a prismatic main body with rectangular bases comprising a tube bundle (5) housed in a shell (6) made of die-cut and stamped plate.
  • the tube bundle (5) extends along a longitudinal direction which will be identified as X-X', like in the first embodiment.
  • the tube bundle (5) is formed by stacking flat tubes configured from pairs of stamped and die-cut plates.
  • Each of the tubes of the tube bundle (5) has an expansion (5.1) of their ends with a rectangular configuration according to their section, such that it is in this expansion (5.1) where the consecutive tubes are supported in the stack.
  • the expansion (5.1) has two effects, the first is the spacing between consecutive tubes for defining the passage channels of the second fluid (12), and the second effect, i.e. the entry and exit of the first fluid (11), occurs through the openings defined with the expansion (5.1), maximizing the entry area into the tube bundle (5) with respect to the front area of said tube bundle (5).
  • the expansion (5.1) is also responsible for closing the inner space defined by the shell (6) at the ends according to the longitudinal direction X-X'.
  • Figure 8 shows a longitudinal section of the second embodiment, wherein this section transversely sections each of the tubes of the tube bundle (5). Due to the particular application of the condenser of this second embodiment, the tubes are flat and very narrow, leaving an also very narrow space between tubes.
  • the section of Figure 10 does not explicitly show the configuration of the tube bundle since there is a folded sheet between tubes for configuring fins for improving the heat exchange and another similar sheet inside the tubes, generating both of them an excessive amount of lines that would hinder seeing the section.
  • Both the inlet (I) for the first fluid through the openings of the expansions (5.1) of the tubes of the tube bundle (5) and the outlet (0) for the first fluid in the expansions (5.1) of the opposite end are identified in said Figure 8 .
  • the inlet and outlet (I, 0) for the first fluid cover the entire transverse area except the thicknesses of the tubes of the expansion (5.1).
  • the configuration of the device is symmetrical with respect to a central transverse plane, hence in Figures 7 , 9 and 10 showing a detail of one end of the device, two reference numbers referring to the same component, regardless of if it is of one end or the other, are indicated.
  • this figure shows the main body of the heat exchanger located between two second manifolds (9, 10) intended for the entry and exit, respectively, of the first fluid (11).
  • the fluid in vapor phase enters through the second inlet manifold (9) of the first fluid (11), gains access to the inside of the stacked tubes of the tube bundle (5) through the inlet (I) for the first fluid; and after going through the tube bundle (5) it exits through the outlet (0) for the first fluid into the second outlet manifold (10) to gain access, once it has changed to the liquid phase, to the next component of the heat recovery system.
  • the second fluid (12) enters through a first tubular inlet segment (7, 8) which is attached to a first inlet manifold (3, 4).
  • the first manifold (3, 4) is located close to the inlet (I, 0) for the first fluid and positioned between the tubular inlet segment (7, 8) and the shell (6).
  • the first manifold (3, 4) has a support base (3.1, 4.1) configured in the form of a triangle with rounded vertexes, with a larger side and two smaller sides having equal dimensions.
  • the larger side of the base (3.1) is arranged adjacent to the end comprising the inlet (I) for the first fluid, and the opposite vertex, the vertex where the two smaller sides converge, is positioned on the side pointing towards the center of the device.
  • the front projection view in Figure 9 shows how the first tubular inlet segment (7) is located on the side of this same vertex.
  • the first manifold (3, 4) internally configures a chamber for access into the tube bundle (5); nevertheless, a extension (6.1) of the shell (6) establishes a partial closure of this fluidic communication between the internal chamber formed by the first manifold (3, 4) and the inside of the shell (6).
  • the fluidic communication between the first manifold (3, 4) and the inside of the shell (6) is through a slot (6.2), which in this case is elongated, having a constant width, oriented transverse to the longitudinal direction X-X'.
  • the spacing between the slot (6.2) and the inlet (I, 0) for the first fluid allows the base (3.1, 4.1) to sit in the shell (6.1) surrounding the slot (6.2).
  • the base (3.1, 4.1) not only surrounds the slot (6.2) but also leaves space inside the first manifold (3, 4) to house the extension (6.1) of the shell (6).
  • the first tubular inlet segment (7, 8) has an orientation perpendicular to the surface of the shell (6) where the first manifold (3, 4) is fixed.
  • the front view allows seeing the projection of the first tubular inlet segment (7, 8) following a direction coinciding with the path of the flow in the operating mode.
  • This projection allows seeing how the extension (6.1) of the shell (6) is interposed at least partially, in this case almost in its entirety, in this path of the flow.
  • the inflow through the first tubular inlet segment (7, 8) is deflected by the extension (6.1) of the shell (6) and distributed homogenously along the entire length of the slot (6.2).
  • This flow thus diverted allows generating through the slot (6.2) a back flow after surpassing the slot (6.2) with a greater velocity and with a configuration in the form of a laminar flow that sweeps the entire section of the tube bundle (5) preventing stagnation regions and therefore reducing locations where there may be thermal fatigue.
  • the baffle formed by the extension (6.1) of the shell (6) does not require manufacturing additional parts that must first be die-cut and stamped and then welded in complex positions, but rather it is enough to suitably design the position and shape of the slot (6.1), the base (3.1, 4.1) for the seating of the first manifold (3, 4) and the orientation of the first manifold (7, 8) .
  • the first/second tubular inlet/outlet segment (7, 8), or both can be inclined with respect to the surface of the shell (6) on which it is fixed by means of the first manifold (3, 4).
  • said first/second tubular inlet/outlet segment (7, 8), or both can be inclined towards the vertex opposite the larger side of the triangular configuration where the extension (6.1) of the shell (6) is located.
  • the seating of the first manifold (3, 4) is located on an expansion (6.4) of the shell (6). Generated inside this expansion (6.4) there is a chamber which allows distributing the flow of the second fluid through the channels between tubes of the tube bundle (5) coinciding with said expansion (6.4).
  • one manifold (3, 4) and the other manifold (9, 10) are configured by die-cutting and stamping.
  • a possible method of manufacturing comprises: die-cutting the plate including the plate corresponding to one manifold (3, 4) and the other manifold (9, 10) plus a plate connecting portion between both manifolds (3, 4; 9, 10); and carrying out an operation of bending this plate connecting portion at a right angle.
  • the bases of one manifold (3, 4) and the other manifold (9, 10) thereby are oriented perpendicular to one another and sit on the wall of the shell (6) and at the inlet/outlet (I, 0) for the first fluid simultaneously.
  • An object of this invention is also an EGR system for a vehicle with an internal combustion engine comprising a heat exchanger according to any of the described configurations.
  • An object of this invention is also a heat recovery system for a vehicle with an internal combustion engine comprising an evaporator or a condenser according to any of the described configurations.
  • Figures 11 to 15 show two additional embodiments of the invention which allow building a heat exchange device with a smaller number of parts. Both embodiments show only the shell, the rest of the components of the heat exchanger having been removed to make visual access of the inside of the device easier.
  • Figure 11 shows an embodiment where the shell (6) is configured in two parts, a first part with a U-shaped cross section and a second part also with a U-shaped cross section but with one of the arms of the U being considerably shorter.
  • the extensions of both parts are identified with the term "arms," the same elements, when not referred to by means of their section configuration, will be identified as extensions.
  • the attachment between both parts of the shell (6) is carried out by overlapping the extensions of both parts at least along a strip according to the longitudinal direction X-X'.
  • the attachment is along a strip according to the longitudinal direction X-X' wherein the end of the extension corresponding to the short arm is stepped towards the inside of the shell (6).
  • the first manifold (3) is configured by means of a bulging zone in the extension of one of the parts of the shell (6), the one located on the outside, in the region overlapping the extension of the other part of the shell (6), such that this second extension is located on the inside.
  • the configuration of the first manifold (3) by means of the extension of the shell (6) is carried out through a deep-drawing operation giving rise to a bulging zone.
  • the bulging zone is flat with a plane parallel to the extension (6.1) located inside the first manifold (3).
  • the extension (6.1) of the shell (6) is configured as part of the extension located inside the overlap going into the cavity of the first manifold (3).
  • the shell (6) thereby comprises on the outside an extension containing the first manifold (3) and on the inside the extension (6.1) of the inner extension overlapping the outer extension and acting as a baffle for the flow of the second fluid (12).
  • Both the outer and inner extensions are overlapping and attached, for example by means of brazing, in the area where the first manifold (3) is not located.
  • Other examples of welding applicable to this attachment are: laser, resistance or TIG welding.
  • Figure 12 shows the same embodiment but in this view a section has been applied according to two perpendicular planes, one parallel to the longitudinal axis X-X' and the other one transverse, to allow observing the inside of the first manifold (3) formed by overlapping two extensions of the shell (6), as well as the presence of the slot (6.2) establishing the fluidic communication between the inside of the first manifold (3, 4) and the inside of the shell (6).
  • This particular configuration allows configuring the first manifold (3), the second manifold (4) or both (3, 4) from the plate of the shell (6), this solution being applicable to any of the embodiments described up until now.
  • the support base (3.1) of the first manifold (3) can be identified with the perimetral region of the first manifold (3) where there is overlap between the plate of the extension of the shell (6) located on the outside and the plate of the extension of the shell (6) located on the inside.
  • the embodiment shown in Figures 11 and 12 comprises the inlet for the second fluid (12) at opposite ends according to the longitudinal direction X-X'.
  • the second fluid (12) thus flows through the inside of the shell (6) along the entire length of the tube bundle (5).
  • the inlet for the second fluid (12) is located at the same end, according to the longitudinal direction X-X', where the inlet for the second fluid (12) is located.
  • the configuration of the extensions of the two U-shaped parts configuring the shell (6) are like those of the preceding embodiment, but the first manifold (3) has a bulged region with a larger extension covering virtually the entire flat surface of the shell (6) where the inlet for the second fluid (12) is located.
  • the first manifold (3) configured this way also increases the dimensions of the extension (6.1) such that a circulation channel having a flat configuration is established inside of the first manifold (3).
  • the circulation channel goes from the inlet for the second fluid (12) through the tubular inlet segment (7) to the access slot (6.2) of the second fluid (12) into the shell (6) in which the tube bundle of the heat exchanger (5) is housed.
  • the configuration of the channel can be narrower forming a conduit between the plate of the extension located on the outer side and the plate of the inner extension (6.1). Nevertheless, the larger dimensions of the channel like that shown in Figures 13 to 15 establish a larger passage section and therefore smaller pressure drops.
  • the larger area of the plate of the inner extension (6.1) allows including more than one a slot (6.2) for allowing the passage of the second fluid (12), for example to zones which would otherwise be stagnation regions.
  • Figure 14 shows a cross section which allows seeing the transverse slot (6.2) located inside the first manifold (3).
  • Figure 15 is a section having larger dimensions which allows seeing the channel formed by the inside of the first manifold (3). The direction in which the second fluid can flow has been identified by means of arrows.
  • access of the tubular segment (7, 8) in fluidic communication with the first manifold (3) is spaced from the slot (6.2) according to the longitudinal direction X-X' such that the extension (6.1) and the first manifold (3) define a channel for the passage of the second fluid (12).
  • the first manifold (3) is configured by means of overlapping two extensions of the shell (6) wherein it is the outer extension that is bulged such that both extensions are spaced from one another.
  • the inner extension is bulged inwardly to allow for the two spaced extensions.
  • the region bulged towards the inside of the shell (6) is what comprises both the deflecting extension (6.1) and the slot (6.2).
  • the two extensions of the shell (6) are attached to one another and the first tubular inlet segment (7) or the second tubular outlet segment (8) is in fluidic communication with the first manifold (3).
  • Figures 16 , 17 and 18 show another embodiment where the tubular inlet segment (7) is located on one side of the shell (6).
  • the passage channel formed between the extensions of the two U-shaped parts which are overlapping and spaced from the shell (6) are laterally extended from the face on which the slot (6.2) is located, such that it allows access of the second fluid (12) into heat exchanger from this side through the tubular inlet segment (7). That is, the region of the two extensions that are overlapping and spaced from one another extends between two adjacent faces of the shell (6).
  • Figure 17 is a partial section which allows showing the position of the slot (6.2), located at one end of the heat exchanger and arranged transverse to the longitudinal direction (X-X'), and also allows showing the extension of the flat channel towards the side of the heat exchanger where the tubular inlet segment (7) is located.
  • Figure 18 shows a section having larger dimensions for seeing the larger dimensions of the flat channel formed between the extensions of the shell (6) which are overlapping and spaced from one another to give rise to said flat channel.
  • FIGs 19 to 23 show a new embodiment of a two-stage exchanger not within the scope of the invention.
  • Two-stage exchangers reduce the length of the tube bundle by splitting it into two segments arranged essentially parallel to one another, an outgoing segment and another return segment.
  • the embodiment uses this two-stage configuration to incorporate an embodiment of the invention, in which the first fluid (11) exiting from the outgoing segment changes direction through a direction-changing manifold (13).
  • This embodiment incorporates various solutions that have been previously described and some solutions that are also applicable to embodiments that have already been described.
  • the tube bundle is differentiated in two groups separated by a wall (6.5), a first group of tubes for the outgoing segment for the first fluid (11) and a second group of tubes for the return segment for the first fluid (11) through which said first fluid (11) flows after changing direction through the direction-changing manifold (13).
  • This direction-changing manifold (13) redirects the first fluid (11) from the outlet of the first outgoing segment to the inlet of the second return segment.
  • Figure 20 is a top view of a section which allows seeing the upper face of the shell.
  • Figure 20 shows arrows indicating the direction of flow of both the first fluid (11) and the second fluid (12). It has already been indicated that the first fluid (11) has a first path through a first segment and a second path through a second segment. These segments are the two defined inside the chambers existing inside the shell (6) separated by the wall (6.5). The change in direction is depicted in this drawing by means of a hollow, two-way arrow since the circulation direction depends on if the heat exchanger works in co-current or on if it works in counter-current. The rest of the arrows show the path of the second fluid (12).
  • first inlet manifold (3) and the first outlet manifold (4) are longitudinally extended along most of the length of the heat exchanger such that they generate a flat channel.
  • Figure 20 shows, by means of a circle with a dashed line, the inlet (I) and the outlet (0) given that they are not seen due to the section.
  • the second fluid (12) enters through the tubular inlet segment (7), being deflected by the extension of the shell (6.1) to be driven through the flat channel to the other end of the heat exchanger.
  • the slot (6.2) is located at the end of the first inlet manifold (3). Given that the path is parallel to the longitudinal direction (X-X') of the heat exchanger, the second fluid tends to maintain a parallel path.
  • the slot (6.2) is U-shaped, giving rise to a tab (6.2.1) which is bent towards the inside of the shell (6) housing the tube bundle.
  • the mainly longitudinal path of the second fluid (12) into the first inlet manifold (3) is indicated with a continuous arrow.
  • the passage from one of the chambers defined by the wall (6.5) to the other chamber occurs at the longitudinal ends of the wall (6.5) given that said wall (6.5) does not reach the end.
  • the spacing with the end baffles establishes a passage window (6.5.1) which can be enlarged, as occurs at one of the ends depending on the flow that is to be allowed in each of said ends.
  • Figure 21 is a front section view coinciding with the second slot (6.2) which shows the path of the second fluid (12) through the first manifold (3) until exiting through the tubular outlet segment (8).
  • This figure shows the window (6.5.1) facilitating the passage from one of the chambers defined by the separation wall (6.5) to the other chamber, as well as the passage established at the opposite end since the wall (6.5) does not reach said end.
  • Figure 22 is a section view like that of Figure 21 , but the plane of section passes through the first slot (6.2). In this case, the circulation direction of the second fluid (12) is the opposite shown by the arrows.
  • This section shows the curvature of the tab (6.2.1) towards the inside of the chamber defined by the wall (6.5) on the inside of the shell (6).
  • Figure 23 is a cross-section view of the embodiment showing the central arrangement of the wall (6.5), the tab (6.2.1) formed by means of the slot (6.2) with the curvature towards the inside of the chamber, the other outlet slot (6.2) for the second fluid (12) and the flat channels established by the first inlet manifold (3) and the first outlet manifold (4).
  • the solution of establishing a deformation, for example by deep-drawing, in the plate of the extension (6.1) of the shell (6) around the slot (6.2) to achieve deflection of the flow passing through the slot (6.2) is applicable to any of the embodiments described above, and particularly by using a U-shaped slot to obtain a tab (6.2.1).
  • the shell as having a tubular configuration, it can be manufactured using two U-shaped parts with overlapping extensions, both for the attachment of the two U-shaped parts and for the formation of the first manifolds (3, 4) .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (19)

  1. Échangeur de chaleur pour le transfert de chaleur entre un premier fluide (11), un fluide chaud, et un second fluide (12), un fluide froid, dans lequel ledit échangeur de chaleur comprend :
    - un faisceau de tubes d'échange de chaleur (5) s'étendant selon une direction longitudinale (X-X') entre une entrée (I) pour le premier fluide dans le faisceau de tubes et une sortie (O) pour le premier fluide du faisceau de tubes, dans lequel le faisceau de tubes d'échange de chaleur (5) est prévu pour entraîner l'écoulement du premier fluide (11),
    - une coque (6) logeant le faisceau de tubes d'échange de chaleur (5) et s'étendant selon la direction longitudinale (X-X') au moins entre l'entrée (I) pour le premier fluide et la sortie (O) pour le premier fluide, dans lequel la coque (6) est prévue pour entraîner le second fluide (12) à travers l'espace défini entre les tubes du faisceau de tubes d'échange de chaleur (5) et la coque (6),
    - un segment d'entrée tubulaire (7) pour l'entrée du second fluide (12) dans la coque (6) et un segment de sortie tubulaire (8) pour la sortie du second fluide (12) de l'intérieur de la coque (6), dans lequel :
    - l'échangeur de chaleur comprend au moins un premier collecteur (3, 4) positionné, selon la direction longitudinale (X-X'), à proximité de l'entrée (I) pour le premier fluide ou bien la sortie (O) pour le premier fluide, et positionné :
    ∘ soit entre le premier segment d'entrée tubulaire (7) et la coque (6),
    ∘ soit entre le second segment de sortie tubulaire (8) et la coque (6),
    ∘ ou bien aux deux emplacements ;
    - la coque (6) a une fente (6.2) pour le passage du second fluide (12) entre l'intérieur du premier collecteur (3, 4) et l'intérieur de la coque (6) dans laquelle le faisceau de tubes de l'échangeur de chaleur (5) est logé, cette fente (6.2) étant espacée de l'entrée/sortie (I, O) correspondante pour le premier fluide dans laquelle ledit premier collecteur (3, 4) est positionné,
    - la coque (6) a une extension (6.1) dans le premier collecteur (3, 4) de sorte que ce prolongement (6.1) établit une fermeture partielle dans la communication fluidique entre l'intérieur du premier collecteur (3, 4) et l'intérieur de la coque (6) dans laquelle le faisceau de tubes de l'échangeur de chaleur (5) est logé,
    caractérisé en ce que :
    - la fente (6.2) a une configuration essentiellement allongée selon une direction principale et a une largeur variable.
  2. Échangeur de chaleur selon la revendication 1, dans lequel l'extension (6.1) est positionnée de sorte qu'elle est au moins partiellement intercalée dans la trajectoire de l'écoulement entraîné dans le mode opératoire par le segment tubulaire d'entrée/sortie (7, 8) fixé sur le premier collecteur (3, 4).
  3. Échangeur de chaleur selon la revendication 1 ou 2, dans lequel le premier collecteur (3, 4) a une base (3.1, 4.1) prévue pour être supportée sur la coque (6), dans lequel ladite base (3.1, 4.1) a :
    - une configuration essentiellement triangulaire avec un grand côté et deux petits côtés, avec les sommets de la configuration triangulaire qui sont arrondis,
    - le grand côté est perpendiculaire à la direction longitudinale (X-X') et est positionné sur le côté correspondant à l'entrée/sortie (I, O) pour le premier fluide dans laquelle le au moins un premier collecteur (3, 4) est positionné, et
    - le sommet opposé à ce grand côté est à l'endroit où au moins l'extension (6.1) de la coque (6) dans le premier collecteur (3, 4) est positionnée.
  4. Échangeur de chaleur selon la revendication 1 ou 2, dans lequel le premier collecteur (3, 4) a une base (3.1, 4.1) prévue pour être supportée sur la coque (6), dans lequel ladite base (3.1, 4.1) :
    - a une configuration essentiellement allongée selon une direction principale,
    - a des extrémités arrondies, et
    - la direction principale le long de laquelle elle s'étend, est essentiellement perpendiculaire à la direction longitudinale (X-X').
  5. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel la fente (6.2) a une configuration essentiellement allongée selon une direction principale et a une largeur diminuant d'une extrémité à l'extrémité opposée.
  6. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel le premier segment tubulaire (7), le second segment tubulaire (8) ou à la fois les segments tubulaires d'entrée/sortie (7, 8) sont inclinés par rapport à la surface de la coque (6) sur laquelle ils sont fixés au moyen du premier collecteur (3, 4).
  7. Échangeur de chaleur selon l'une quelconque des revendications précédentes et selon les revendications 4 à 6, dans lequel le premier segment tubulaire (7), le second segment tubulaire (8) ou à la fois les segments tubulaires d'entrée/sortie (7, 8) sont inclinés vers l'extrémité de la fente plus large.
  8. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel le premier segment tubulaire (7) et le second segment tubulaire (8) sont décentrés par rapport à l'axe longitudinal central et sur les côtés opposés, et dans lequel au moins le segment tubulaire (7, 8) positionné dans le premier collecteur (3, 4) intérieurement prévu avec une fente (6.2) ayant une largeur variable est décentré vers l'extrémité de la fente plus large.
  9. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel la région de la coque (6) sur laquelle le second collecteur (9, 10) est supporté et forme l'extension (6.1) se présente sous la forme d'une expansion (6.4), augmentant l'espace à l'intérieur de la coque (6).
  10. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel le premier collecteur (3, 4) a une base (3.1, 4.1) prévue pour être supportée sur la coque (6) formée au moyen d'une bride périmétrale ou bien au moyen d'un bord de support.
  11. Échangeur de chaleur selon l'une quelconque des revendications précédentes, comprenant en outre :
    - un second collecteur d'entrée (9) pour le premier fluide (11) positionné sur le côté de l'entrée (I) pour l'entrée du premier fluide dans le faisceau de tubes et configuré de sorte que dans le mode opératoire, le premier fluide (11) entrant par une ouverture d'entrée (9.1) dudit collecteur (9) est entraîné dans les tubes du faisceau de tubes d'échange de chaleur (5),
    - un second collecteur de sortie (10) pour le premier fluide (11) positionné sur le côté de la sortie (O) pour la sortie du premier fluide du faisceau de tubes et configuré de sorte que, dans le mode opératoire, le premier fluide (11) sortant de l'intérieur des tubes du faisceau de tubes d'échange de chaleur (5) est entraîné vers une ouverture de sortie (4.1) dudit collecteur (4).
  12. Échangeur de chaleur selon l'une quelconque des revendications précédentes et selon la revendication 11, dans lequel le premier collecteur (3, 4) et le second collecteur (9, 10) agencés au niveau de la même extrémité selon la direction longitudinale (X-X') sont configurés en une seule pièce.
  13. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel la coque (6) est configurée en au moins deux parties en forme de U et fixées entre elles par le biais des pattes du U.
  14. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel la coque (6) représente deux extensions se chevauchant, dans lequel :
    - l'extension externe, l'extension interne ou les deux est/sont configurée(s) de sorte que les deux extensions sont espacées l'une de l'autre, configurant le premier collecteur (3),
    - au moins dans la région périmétrale du premier collecteur (3), les deux extensions de la coque (6) sont fixées entre elles ; et
    - le premier segment d'entrée tubulaire (7) ou le second segment de sortie tubulaire (8) est en communication fluidique avec le premier collecteur (3).
  15. Échangeur de chaleur la revendication 14, dans lequel la région des deux extensions qui se chevauchent et espacées l'une de l'autre s'étend entre deux faces adjacentes de la coque (6).
  16. Échangeur de chaleur selon la revendication 14 ou 15, dans lequel l'accès :
    - soit du segment d'entrée tubulaire (7) en communication fluidique avec le premier collecteur (3),
    - ou bien du segment de sortie tubulaire (8) en communication fluidique avec le premier collecteur (4),
    - ou bien des deux,
    sont espacés de leur fente (6.2) correspondante selon la direction longitudinale X-X' de sorte que l'extension (6.1) et le premier collecteur (3) définissent un canal pour le passage du second fluide (12).
  17. Échangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel une région de l'extension (6.1) entourant la fente (6.2) représente une déformation pour dévier l'écoulement du second fluide (12) passant par ladite fente (6.2).
  18. Échangeur de chaleur selon l'une quelconque des revendications précédentes, configuré dans deux passages comprenant en outre :
    - une paroi (6.5) pour établir deux chambres séparant les tubes du faisceau de tubes en deux groupes, dans lequel la fente (6.2) du premier collecteur d'entrée (3) est en communication fluidique avec l'une des chambres et la fente (6.2) du premier collecteur de sortie (4) est en communication fluidique avec l'autre chambre ;
    - un collecteur de changement de direction (13) pour placer la sortie des tubes du premier groupe de tubes en communication fluidique avec l'entrée des tubes du second groupe de tubes.
  19. Système de EGR ou à récupération d'énergie pour un véhicule avec un moteur à combustion interne comprenant un échangeur de chaleur selon l'une quelconque des revendications précédentes.
EP16382220.8A 2016-05-19 2016-05-19 Dispositif d'échange de chaleur Active EP3246647B1 (fr)

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EP16382220.8A EP3246647B1 (fr) 2016-05-19 2016-05-19 Dispositif d'échange de chaleur
US15/596,646 US20170336147A1 (en) 2016-05-19 2017-05-16 Heat exchange device
CN201710352163.XA CN107401939A (zh) 2016-05-19 2017-05-18 热交换装置

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CN107401939A (zh) 2017-11-28

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