EP1654508B2 - Echangeur de chaleur et procede de fabrication dudit echangeur - Google Patents

Echangeur de chaleur et procede de fabrication dudit echangeur Download PDF

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Publication number
EP1654508B2
EP1654508B2 EP04763632.9A EP04763632A EP1654508B2 EP 1654508 B2 EP1654508 B2 EP 1654508B2 EP 04763632 A EP04763632 A EP 04763632A EP 1654508 B2 EP1654508 B2 EP 1654508B2
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EP
European Patent Office
Prior art keywords
plates
heat exchanger
profile
plate
another
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EP04763632.9A
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German (de)
English (en)
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EP1654508B1 (fr
EP1654508A1 (fr
Inventor
Peter Geskes
Jens Richter
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Mahle Behr GmbH and Co KG
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Mahle Behr GmbH and Co KG
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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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • F28D2021/0049—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for lubricants, e.g. oil coolers
    • 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
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0089—Oil coolers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/355—Heat exchange having separate flow passage for two distinct fluids
    • Y10S165/356—Plural plates forming a stack providing flow passages therein
    • Y10S165/364—Plural plates forming a stack providing flow passages therein with fluid traversing passages formed through the plate
    • Y10S165/372—Adjacent heat exchange plates having joined bent edge flanges for forming flow channels therebetween

Definitions

  • the present invention relates to a heat exchanger according to the preamble of claim 1, as is used in particular in vehicles as an oil cooler.
  • a heat exchanger is made of DE 199 59 780 A1 known.
  • So-called plate heat exchangers which are formed from a stack of plates lying side by side. Cavities are formed between the plates, through which a first or a second medium flows alternately.
  • the first medium for example, cooling water and the second medium being the working medium to be cooled - in the case of an oil cooler of an internal combustion engine, the engine oil -
  • a cooling device such as a vehicle air conditioning system is also conceivable, one of which both media is the coolant and the other is the refrigerant.
  • the plates are profiled so that contact points occur between the plates.
  • the plates are attached to each other in the area of the contact points.
  • the plates lie against one another on the outside so that the cooling medium or the working medium flows exclusively through the cavity.
  • the first and second medium are each fed through a corresponding inflow line and led away via a drain line.
  • Inflow lines and outflow lines each serve as collecting lines, in which the fluid flow of all corresponding cavities is fed in or out.
  • turbulence-increasing internals for improving the heat transfer and for increasing the surface area are usually introduced into the fluid channels and firmly connected to the heat-transferring plate.
  • the strength property of the cooler is greatly improved.
  • a disadvantage of such turbulence plates is that during the production of the passage openings, chip formation easily occurs, which can lead to contamination of the medium flowing through.
  • dirt easily accumulates in the area of the turbulence plates. This can undesirably impede the flow through the cavity.
  • they represent an additional component to be manufactured, which increases the cost of the heat exchanger due to increased manufacturing costs and material costs.
  • a heat exchanger as is used in particular as an oil cooler in the field of motor vehicles, is formed from interconnected plates. Cavities which are closed off from the outside are formed between the plates. The cavities are alternately via at least one inflow and outflow line with the first and second medium supplied and are also flowed through by the appropriate medium.
  • the plates are profiled in such a way that contact points occur between the respective profiles of the plates. The plates are connected to one another in the area of these contact points. The plates are designed in such a way that the flow of the first or second medium forming between the plates does not run in a straight line from the corresponding inflow line to the corresponding outflow line.
  • This measure has the advantage that the medium flowing through is partly redirected several times on its flow path. This improves the distribution of the fluids across the plate width. Depending on the flow behavior (viscosity) of the medium flowing through, turbulent flows may also occur. The repeatedly occurring changes in direction of the fluid in the channel and the eddies that may form in the area of the opening wave channel tear the boundary layer that is formed again and again. This leads to an improved heat transfer.
  • the plates have a repeating wave profile which then runs at least in a direction transverse to the flow direction, which is the straight connection from the entry point of the medium to the exit point.
  • the wave profile is zigzag around this direction.
  • Such a wave profile easily forms flow guide areas which are suitable for guiding the flow of the medium flowing through the corresponding cavity.
  • the flow is thereby deflected several times in an advantageous manner, in particular not only in the plate plane but also out of the plate plane. In areas in which the distance between the plates is different, the flow rate may vary.
  • it is advantageously achieved that the medium as a whole is distributed over the entire surface of the plates, thus making the best possible use of the entire heat exchange surface.
  • the wave profile between flow regions has straight legs, the course of the wave profile being characterized by the leg length of the legs, the leg angle between the legs and the profile depth of the wave profile.
  • the cross section of the profile of a corrugated profile is determined by the course in the region of the legs and in the region of curvature, preferred configurations being able to provide a deviation in the cross-sectional shape in these regions.
  • the zigzag wave profile is characterized by the leg length, the leg angle between adjacent legs and the profile depth.
  • the leg length is in the range from 8 to 15 mm, preferably in the range from 9 to 12 mm.
  • Typical values of the profile depth - which is measured, for example, from the distance between a shaft crest and the plate center plane - are in the range from 0.3 to 1.5 mm.
  • a profile depth between 0.5 and 1 mm can be advantageous for many applications, values of approximately 0.75 mm being preferred.
  • the leg angle between two legs of the wave profile is preferably between 45 ° and 135 °. Values around 90 ° in particular represent a good compromise with regard to the distribution of the fluid, flow rate and flow rate of the heat exchanger.
  • leg length and the leg angle influence on the one hand the flow control function of the wave profile, but on the other hand also the arrangement of points of contact between adjacent plates, which are necessary for the stability of the heat exchanger.
  • the inherent rigidity of the plates against pressurization by the media can be without mutual support cannot be guaranteed if the material thickness of the plate is chosen to be low, as is desirable in many applications for reasons of weight saving and heat exchange.
  • the plates are connected in the area of the contact points by brazing, for which purpose the plates are coated at least on one side with a soldering aid, such as solder.
  • the leg length and leg angle are preferably selected as a function of the medium flowing through and its viscosity. Leg length and leg angle have a major influence on the flow velocities and the associated heat exchange, so that they can be adapted to the respective purpose.
  • the values mentioned above relate in particular to the use of heat exchangers as an oil cooler in vehicles, where the heat exchange takes place between engine oil and cooling water. In addition, they are of course also dependent on the dimensioning of the plates and the space resulting from the distance between the plates.
  • the shape of the wave profile is essentially determined by the shape of the cross section perpendicular to the outer edge of the profile in this area and by the sequence of the profiles determined by the division in the course transverse to the direction of extension of a wave profile across the plate.
  • Preferred refinements provide for a constant division, that is to say a fixed distance between any two adjacent wave profiles.
  • the shape of the wave profile is particularly advantageous if it has a flat area on the outside of the wave back.
  • the flat area in particular has a width of 0.1 to 0.4 mm.
  • the flat area enables good, flat contact of adjacent plates with each other and thus an easy and stable production of the Support or connection - as by brazing - of adjacent plates.
  • the material of the plates is preferably aluminum. This material has the advantage of having a low density and at the same time making it possible to produce the wave profile in a simple manner, for example by embossing.
  • it can be coated on at least one side with soldering aids such as hard solder. Depending on the selection of the soldering aid and the layer thickness of the application of the soldering aid, a coating on both sides with soldering aid can also be provided.
  • the coating with soldering aids is intended, in particular in the area of the edges and the inflow and outflow lines in the block, to reliably establish a fluid-tight connection of two plates to one another in a joining process using a joining tool (brazing furnace) without the use of further aids or auxiliaries.
  • the plates have bores which serve as inflow and outflow lines in the area of the heat exchanger and the bore axis of which runs perpendicular to the plane of the plate.
  • the holes are drilled in an area that is raised from the base plane of the plates.
  • the raised area is preferably so raised that there is a tight connection between the raised area and the subsequent further plate in every second plate space, so that a fluidic connection between the bores and the plate space occurs only in every second plate space. This measure enables fluid supply and discharge from the plate interspaces without the use of lines, so that the flow of cooling medium or working medium alternates between them.
  • the fluid-tight system between an elevated area and an adjacent plate can be achieved not only by positive locking but also by other connection technology, such as brazing.
  • the raised area has, in particular, a preferably flat contact section which is in contact with a preferably flat contact edge of the adjacent plate, to which a fluid-tight connection results.
  • the raised area and the bores in the raised area can not only have a circular cross section, oval or slot-like designs are also possible and advantageous.
  • the longer of the two axes of the slot-like design should preferably be arranged transversely to the main flow direction of the fluid. This measure also serves to improve the heat exchange between the two media, since a larger heat transfer area then remains with the same overall expansion of the plates.
  • distribution channels are provided in the area of the inflow lines and the bores assigned to the inflow lines, which are also designed as a wave profile. It corresponds to particularly preferred further developments of the invention if the wave profile of the distribution channels differs from the other wave profiles with regard to the characteristic sizes of the wave profile.
  • the corrugated profile of the distribution channels has in particular a leg angle that is less than 45 ° and in particular in the range of approximately 5 ° and approximately 25 °. Both an abrupt and a continuous transition in the profile design between the distributor profile and the wave profile can be formed in other plate areas.
  • the distribution channels take on the task of distributing the fluid flow as evenly as possible over the entire width of the plate.
  • Flow channels can also surround the raised areas to improve the distribution of the medium over the entire surface of the heat exchanger.
  • the flow channels are preferably formed by a section without a wave profile, which is guided in particular in a ring-like manner around the raised area. A section of reduced flow resistance is thus formed, into which several wave profiles open, so that this also fulfills a distribution function for the medium.
  • a heat exchanger can be formed, in particular, from a stack of such plates which are configured identically to one another. This is because, in particular, it is possible for plates that are adjacent to one another to be rotated by 180 degrees to one another, the axis of rotation extending perpendicular to the plate plane.
  • This type of stack of plates is particularly advantageous if the bores assigned to the inflow lines are formed from raised locations and these are to be assigned alternately to two different line routings.
  • the elevations in the area of the inflow lines can in particular be designed as an essentially frustoconical dome. Alternatively, there are dome-shaped elevations which have an elliptical cross section.
  • the plates can be designed identically to one another, corresponding to one another, or similar or different. Plates which are identical to one another have identical properties with regard to the characteristic properties of the wave profile and the shape of the wave profile on. Corresponding plates are identical in structure to one another, but it is possible that the plates have, for example, mutually different leg angles. Corresponding plates preferably have a mutually different shape of the wave profile and / or values characterizing values different from one another, but are corresponding to one another with regard to the formation of the edge and the formation of the front and back of the plates.
  • the alternating use of, for example, two corresponding plates, which differ in the characteristic sizes only by different leg angles, has the advantage that the position and relative position of points of contact between the plates in the profiled area with regard to the required rigidity and the required flow in are easy to optimize.
  • connection between the plates is made in particular by brazing.
  • the plates have a bent edge whose height is selected such that at least two plates adjacent to one another abut one another in this edge region and overlap.
  • the number of overlapping plates in the edge area can be up to five. The greater the number of overlapping plates, the stiffer is the wall formed in this way and which closes the heat exchanger to the outside. At the same time, this supports the manufacture of a permanently stable, robust, fluid-tight closure of the panels to the outside.
  • Preferred further developments provide that the wave profile extends into the edge and in particular over its entire width. When designing the wave profile, care must be taken to ensure that the plates remain stackable, which is due to the fact that the wave profile runs in the edge area to match the mounting position of two neighboring panels to each other.
  • the wave profile extends into the edge when the wave profile ends in the root region of the offset, so that the profile with its profile depth extends into the edge.
  • the root of the edge lies in an area free of wave profiles, since the edge can then be bent in an area not stiffened by a profile.
  • the groove which forms between the edge and the wave profile area is as narrow as possible.
  • it is chosen so narrow that a solder flow occurs during brazing, which closes this channel completely or at least to such an extent that only a negligible amount of medium flows through the channel.
  • the channel must be designed in such a way that it does not serve as a bypass channel for the medium and a significant proportion of the media flows through the channel instead of in the area of the wave profile.
  • At least one end face of the heat exchanger without a profile end plate is arranged.
  • the end plate without profile on the outside in particular has flanges as connection points.
  • the end plates can in particular also have a greater material thickness than the other plates and thus represent an in particular stiffening, stabilizing element which forms a housing part which closes the end faces to the outside.
  • the side walls of the housing, which close off the heat exchanger from the outside, are formed over the edge that delimits the plates and that coincides with the edge adjacent plates overlap.
  • the edges are connected to one another in a fluid-tight manner, which can be done in particular by brazing.
  • the hydraulic diameter represents a ratio between the flowable channel cross section and the heat exchange area.
  • the hydraulic diameter hD is defined as four times the ratio of the area ratio Fv to the area density Fd.
  • the hydraulic diameter should remain as constant as possible over the entire main flow direction of the medium. In this way, an improved and possibly a uniform flow through the plate intermediate space, which forms the channel, is achieved.
  • the hydraulic diameter is between 1.1 mm and 2 mm.
  • Preferred values for the hydraulic diameter are around 1.4 mm.
  • the deviation of the hydraulic diameter over the period of profiling a pair of plates preferably not fluctuate by more than 10%, in particular by less than 5%.
  • the selection of the hydraulic diameter also depends on the media flowing in the spaces between the plates. The values mentioned apply to an oil cooler in which water and oil flow through the heat exchanger.
  • the contact points between two adjacent plates of the heat exchanger are evenly distributed over the plate surface.
  • the contact points between two adjacent plates preferably have a surface density of 4 to 7 per cm 2 , particularly preferably 5 to 6 per cm 2 . With such a configuration, sufficient strength of the heat exchanger is possible without an excessive increase in pressure loss.
  • Heat exchangers according to the invention can serve on the one hand as an oil cooler, but also as an evaporator or condenser.
  • the cooling circuit of such a device can not only be used to air-condition a (vehicle) interior, but also to cool heat sources such as electrical consumers, energy stores and voltage sources or charge air of a turbocharger.
  • the heat exchanger is a condenser if, for example, condensation of the refrigerant in an air conditioning system takes place in a compact heat exchanger that is subjected to coolant and the coolant releases the heat in a heat exchanger to air as a further medium.
  • the evaporation or condensation of another medium in a heat exchanger according to the invention can also take place, for example, in applications in fuel cell systems.
  • a method according to the invention for producing a heat exchanger provides that the corrugated profile is produced by embossing the plates, then the plates are stacked accordingly and then connected by brazing.
  • the plates are stacked on top of one another in such a way that two plates adjacent to each other are arranged rotated by 180 degrees.
  • the plates are joined by brazing in such a way that the plates are sealingly connected to one another at their edge and, in particular, adjacent plates are connected at the points of contact of profiles.
  • FIGS. 1a and 1b show the representation of a front or a back of a plate not according to the invention, while the Fig. 2 the representation of a corresponding, from plates according to the Figures 1a and 1b formed stack shows.
  • a plate 10 has a base body 11, which is provided on its front and rear side with a corrugated profile 12, which has been introduced into the base body 11 by stamping.
  • the wave profile 12 is formed from a plurality of legs 10 which are at a leg angle 13 and each have a fixed leg length 15 and connect the curvature region 16 to one another.
  • the wave profile extends across the plate 10. There is a multitude over the length of the plate 10 of wave profiles 12 formed one behind the other, the wave profiles following one another in particular at close spacing and being aligned with one another.
  • the plate 10 has a circumferential cranked edge 17 which laterally delimits the plate.
  • the wave profile 12 extends into the edge.
  • the wave profile 12 can be introduced into the plate 10 by embossing.
  • the embossing can be carried out in such a way that the two sides in the plate 10 have different wavy profiles, in particular the wavy profile 12 on one side can represent the negative of the wavy profile 12 on the other sides, as is the case, for example, in the exemplary embodiment according to FIGS Figures 1 a and 1b can be seen.
  • the cross section of the wave profile 12 is characterized primarily by the fact that it has a wave ridge which forms a flat region which runs parallel to the plate plane.
  • the flat area preferably has a width between 0.1 mm and 0.4 mm.
  • the plate In the area of the corners, the plate has a bore 18 which passes through the plate perpendicular to its plane of progression. Two of the bores are made in a raised area 19. One of the holes serves to supply working medium into the area between two plates, while in particular the diametrically opposite hole serves to drain off working medium. Another pair of holes is used for the inflow and outflow of cooling medium.
  • plates 10 as in the Fig. 2 shown stacked one on top of the other either the lines assigned to the working medium or cooling medium are alternately fluidly connected to the intermediate space 20 between two plates 10, since the raised area 19 of corresponding bores 18 abuts the adjacent plate 10.
  • the bores 18 thus form the feed lines or drain lines for the cooling medium and working medium through a stack 21 of plates.
  • the Fig. 2 shows a perspective view of such a stack 21 of plates 10 according to the Figures 1 a and 1b.
  • Fig. 3 is the sectional view through a stack 21 according to the Fig. 2 shown.
  • Plates 10 abut one another and are stacked one above the other.
  • the cranked edge 17 of adjacent plates abuts one another and is designed in such a way that the edge of several plates each overlaps. In order to achieve a fluid-tight connection between the edge 17 of two adjacent plates, these are connected to one another by brazing.
  • two mutually adjacent plates abut each other in different areas of their wave profiles 12. In these areas, too, the plates are connected to one another by brazing.
  • the plates can be coated on one side or on both sides with a solder.
  • An intermediate space 20 is formed between two mutually adjacent plates 10, the intermediate space being flowed through either by working medium or by cooling medium.
  • the stack of plates is designed in particular in such a way that working medium and cooling medium flow alternately through the interspaces 20, so that cooling medium and working medium flow around each of the plates 10. A heat exchange between cooling medium and working medium can thus take place across each of the plates 10.
  • the intermediate space 20 is of different internal width at a large number of locations.
  • the repeatedly occurring changes in direction of the fluid in the channel and the eddies that form in the region of the opening wave channel tear the boundary layer that forms again and again. this leads to one, compared to a smooth channel, greatly improved heat transfer.
  • the design of the plates 10 ensures that no linear, rectilinear flow from the supply line to the drain line is possible. Depending on the viscosity of the medium, such a design of the intermediate space 20 can also result in wholly or partly turbulent flows and thus an improved heat exchange between the working medium and the cooling medium.
  • the course of the wave profile 12 transversely to the extent of the plate 10 also guides the corresponding medium over the entire width of the plate 10, so that the utilization of the heat exchange surface which a plate 10 offers is improved, thereby reducing the efficiency of such a plate Heat exchanger is further increased.
  • An essential guiding element for the flow guidance is also to be seen in the fact that, between two adjacent plates 10, like a Dalton grid, there are always contact points which act as a flow obstacle and flow deflection points. In addition, these points of contact act to support the plates against one another and thus have a stabilizing function for the plates 10, in particular with regard to the determination behavior of the plates 10 Fig. 8
  • the arrangement of the contact points of the profiles of adjacent plates is important. These result from the wave profiles of mutually facing sides of the plates and from the profile profiles.
  • a uniform hydraulic diameter ensures a uniform flow of the fluid across a wave profile and across the entire width of the plate gap.
  • a hydraulic diameter that is optimized for the application is achieved by constructive design selection of the shaft profile.
  • the Fig. 4 shows an enlarged view of a plate 10 with a wave profile 12, which is formed by the legs 14, which have a leg angle 13 of 45 ° to each other.
  • the plate 10 is delimited by a cranked edge 17, the wave profile 12 extending into the area of the edge 17.
  • Distribution channels 22 are formed in the area between the two bores 18, which in particular also extends into the area between the bores 18 and the nearby edge 17.
  • the distribution channels 22 are formed by a corrugated profile 23, which differs from the corrugated profile 12 in the remaining area of the plate 10 with regard to the leg angle and the leg length.
  • the leg angles are in particular in a range below 45 °.
  • the distributor channels 22 lead, in particular, medium entering the corresponding space transversely to the main extent of the plate 10 and thus ensure a uniform distribution of the fluid flow over the entire width of the plate.
  • the bores 18 can also be elongated to increase the cross-section, the elongated axis then preferably extends transversely to the main flow direction H.
  • a profile-free ring area 99 around a dome-shaped area 19 around a channel which connects several wave profiles 23 and distribution channels 22 to one another and ensures a good transverse distribution of medium, since it forms a low-flow area.
  • the ring region 19 has an embossing depth which essentially corresponds to the embossing depth of the wave profile 23.
  • the Fig. 5 shows a top view of an end plate 24, which has four connecting flanges 25, which are aligned with the bores 18 of the plates 10 of a plate stack 21.
  • Such an end plate can be arranged on the one hand or on both sides of the stack 10 and can close it off to the outside.
  • the end plate 24 has no corrugated profile 12 at least on the outside. If a connection plate 24 is arranged on either side of the plate stack, it is possible that one of the two plates has four connection flanges 25 or that one plate has one, two or three connection flanges 25 and the opposite plate has the remaining number of 4 connection flanges 25 .
  • the connection flanges 25 are each assigned to the connection bores.
  • connection flanges 25 serve to connect the external lines for the supply and discharge of working medium and cooling medium.
  • the end plate 24 stiffens the plate stack 21 and forms the front housing wall.
  • the end plate 24 can have an edge 17 which is adapted to the edge 17 of the plates 10.
  • the superimposed edges 17 of the plates form in a plate stack 21, as in the Fig. 2 is shown, the side housing wall of the heat exchanger.
  • a stack of plates according to the Fig. 2 , provided with connecting flanges 25 and an end plate 24 thus forms a heat exchanger.
  • Such a heat exchanger can serve in particular as an oil cooler in a vehicle.
  • the Figure 6 shows a plate stack 21, consisting of a base plate 88, of plates 10 and of a cover plate 89, which has three holes 18, 18a.
  • the bores 18 serve to guide a first medium which is carried out between the plates in such a way that the plate interspaces 20 are flowed through parallel to one another.
  • a second medium enters the plate stack through the hole 18a and exits the plate stack through the hole 18b in the base plate.
  • the flow channels for the second medium are divided into at least two flow paths, which are flowed through in succession and each consist of one or more flow channels, by at least one partition wall arranged between the bores 18a and 18b and not visible from the outside.
  • the flow channels for the first medium are flowed through in parallel.
  • the flow channels for the first medium are likewise divided into at least two flow paths, through which the flow passes one after the other.
  • the 7a to 7d show different orientations of the main flow direction H of the plate gap 20 with respect to the gravitational direction G in the installed position of the heat exchanger, as well as the favorable influence on the distribution of the medium in the plate gap, especially when used as a condenser.
  • the Figures 7a and 7c show the application of an evaporator. From the 7a and 7c it can be seen that the main flow direction H should be transverse or antiparallel to the gravitational direction G, depending on whether the longer L or the narrower side S of the plates is oriented in the gravitational direction G if it is a liquid medium.
  • the gravitation supports a transverse distribution of the medium with respect to the main flow direction.
  • they show 7b and 7d that there is a gaseous Medium is best distributed between the plates 10 if the direction of gravity G counteracts the distribution of the medium between the plates.
  • the Figure 8 shows the hydraulic diameter over an entire wave profile in the main flow direction H, wherein in Fig. 8a the formation of the wave profile 23 with the contact points of adjacent plates 10 shown as circles 98 is shown. It can be seen that the wave profile moves in a bandwidth between 1.2 and 1.6 over the entire period of the pattern resulting from the wave profiles 23 of the adjacent plates and is approximately 1.4 on average.
  • the design of the wave profiles is preferably selected such that the hydraulic diameter in the main flow direction is as constant as possible.
  • Fig. 8a the points of contact between two adjacent plates of the heat exchanger are shown as circles in a plan view of one of the plates. It can be clearly seen that the contact points are evenly distributed over the plate surface.
  • a preferred areal density of the contact points for sufficient strength is 4 to 7 per cm 2 , particularly preferably from 5 to 6 per cm 2 . This is based on 8b, 8c clear.
  • Fig. 8b shows the hydraulic diameter hD of a flow channel between two plates over several profile periods, again in the main flow direction H of the medium.
  • a large areal density of the contact points allows a course to be expected which is shown by the broken curve in Fig. 8b is shown since many points of contact, viewed in the main flow direction H, arranged side by side restrict the flow channel cross section. This is illustrated by the dents 40 in the hydraulic diameter. Due to the configuration according to the invention, in particular the uniform distribution of the contact points these dips are eliminated or reduced, so that the curve for the hydraulic diameter is shown in solid lines. The fewer of these dips in a flow channel, the fewer constrictions for the flowing medium, that is, the pressure loss can be reduced with the same areal density of the contact points.
  • a uniform distribution is achieved in particular in that a region of curvature between two in particular straight legs of a wave profile of a plate does not come to lie exactly above a region of curvature of an adjacent plate.
  • the curvature areas of adjacent plates - as seen in the main flow direction - are offset from one another in such a way that each curvature area is flanked transversely to the main flow direction by two contact points of the two plates, which advantageously have the same or similar spacing from one another as from other contact points and thus release a flow passage between them which allows a significant flow and thus does not contribute to an undesirable extent to a pressure loss in the flow channel formed between the plates.
  • the distance between two points of contact should not be chosen too large, since otherwise local weak points in the strength of the heat exchanger could otherwise form.
  • Fig. 8c a plot of the strength F and the pressure loss DV of a heat exchanger over the density BD of the contact points between two plates is shown.
  • the strength of the heat exchanger increases linearly with the contact point density BD and is reflected in Fig. 8c down as straight line 41.
  • the pressure loss DV in this plot (42) shows a progression; so that there is a maximum 43 at a contact point density for the ratio F / DV of strength F to pressure loss DV BD1 results.
  • the pressure loss is now reduced (44) according to the invention, the aforementioned maximum is increased (45) and possibly shifted to a higher contact point density BD2. It has been shown experimentally that a contact point density of 4 to 7 per cm 2 , preferably of 5 to 6 per cm 2 , leads to good strength with an acceptable pressure loss.
  • a section of a plate 30 of a heat exchanger is shown.
  • the connection points between two adjacent plates are given by the crossing points of the respective wave profiles of the two plates.
  • the leg angle 2b of the outer legs 31 differs from the leg angle 2a of the inner legs 32.
  • the half leg angle b in an edge region of the plate 30 is, for example, 60 ° with a half leg angle of 45 ° in a central region of the plate.
  • Fig. 10 shows a plate 35 of a heat exchanger, in which a wave profile 34 extends to the upturned plate edge 36, a remaining channel 37, which under certain circumstances allows an undesirable bypass flow, has a very small cross section, so that the bypass flow is reducible.
  • solder menisci are formed between the outermost legs 38 of the wave profile 34 and the bent-over plate edge 36, which reduce the edge channel 37 or close it particularly advantageously.
  • the openings 38 of the plate and thus the cross sections of the collecting channels formed thereby are widened in an oval shape.
  • Fig. 11a shows a cross section of a plate 41 of a heat exchanger 42, which is constructed from a plurality of plates 41, as in FIG Fig. 11b pictured.
  • the plates 41 each have a few bores 43 as inflow and outflow lines perpendicular to the plane of the plate, the bores 43 being raised in relation to the base plane of the respective plate 41 in such a way that a fluidic connection from one of the two bores alternates only to every second plate space 44 .
  • Fig. 11b one can see a raised bore 43 in each case on a non-raised area of an adjacent plate 41, so that the height of the raised area is, for example, as large as the height of a wave profile of the plate 41.
  • Fig. 12a shows a cross section of a plate 51 of a heat exchanger 52, which is constructed from a plurality of plates 51, as in FIG Fig. 12b pictured.
  • the plates 51 each have a few bores 53 as inflow and outflow lines perpendicular to the plane of the plate, the bores 53 being raised in relation to the base plane of the respective plate 51 in such a way that a fluidic connection from one of the two bores alternates only to every second plate space 54 .
  • a raised bore 53 lies against a raised bore 53 of an adjacent plate 51, so that the height of the raised area is, for example, only half as large as the height of a corrugated profile of the plate 41.
  • This design may reduce the thinning of the material when producing the raised areas, so that tensile strength, ie internal pressure resistance of the heat exchanger 52 is favorably influenced at least in these areas.

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

Claims (23)

  1. Echangeur de chaleur servant de refroidisseur d'huile pour des véhicules automobiles, où l'échangeur de chaleur est formé par des plaques assemblées entre elles, où des espaces creux fermés vers l'extérieur sont configurés entre les plaques, espaces creux qui sont traversés, de façon alternée, par un premier et un deuxième milieu, à chaque fois via au moins une conduite d'amenée et une conduite d'évacuation, où les plaques sont profilées de manière telle, qu'apparaissent, entre les profils respectifs des plaques, des points de contact dans la zone desquels les plaques sont fixées les unes aux autres, caractérisé en ce que les profils des plaques (10) et leurs points de contact sont configurés de manière telle, que l'écoulement du premier et du deuxième milieu, se formant entre les plaques (10) et à partir de la conduite d'amenée correspondante jusqu'à la conduite d'évacuation correspondante, ne se produise pas de façon rectiligne, où les plaques (10) présentent un profil ondulé (12) se répétant, profil ondulé qui s'étend essentiellement de façon transversale par rapport à la direction principale de circulation (H) et est ondulé en forme de zigzags tout autour de la direction d'étendue, où le profil ondulé (12) présente, entre des zones de courbure, des branches (14) s'étendant de façon rectiligne, où le profil ondulé (12) est caractérisé par la longueur de branche (15) des branches (14), par l'angle de branche (13) formé entre les branches (14) et par la profondeur de profil du profil ondulé, où la forme du profil ondulé est caractérisée par le tracé du profil dans la zone des branches et des zones de courbure, où des profils contigus les uns aux autres se répètent dans une segmentation prédéfinie, où les plaques (10), en tant que conduites d'amenée et conduites d'évacuation, présentent chacune une paire de perçages (18) perpendiculairement au plan des plaques, où les perçages (18) sont saillants par rapport au plan de base de projection, de manière telle qu'une communication fluidique de l'un des deux perçages se produise de façon alternée seulement avec chaque deuxième espace intermédiaire de plaque (20), et où la zone saillante d'au moins une partie des perçages est entourée par une zone de forme annulaire et exempte de profils ondulés, s'étendant tout autour de ladite zone saillante, et où il est prévu, dans la zone des perçages (18) associés aux conduites d'amenée, des canaux de répartition (23) qui sont fournis par un profil ondulé (12) ayant un angle de branche qui est augmenté par rapport à l'angle de branche du profil ondulé.
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que le profil ondulé présente une zone plate sur le côté extérieur d'une queue d'ondulation.
  3. Echangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce que la zone plate est comprise, en coupe transversale du profil ondulé, entre 0,1 mm et 0,4 mm.
  4. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'angle de branche (13), de préférence compris entre 45° et 135°, est de préférence de 90°.
  5. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que la profondeur de profil, comprise entre 0,3 mm et 2 mm, est, dans le cas de milieux liquides, de préférence comprise entre 0,5 mm et 1 mm et, en particulier, comprise entre 0,7 mm et 0,8 mm et, dans le cas de milieux gazeux, est de préférence dans la plage comprise entre 0,6 mm et 2 mm, et en particulier est de 1,5 mm.
  6. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que la longueur de branche (15) est dans la plage comprise entre 8 mm et 15 mm et, en particulier, dans la plage comprise entre 9 mm et 12 mm.
  7. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le profil ondulé (12) est configuré comme un matriçage en creux dans la plaque (10), où les plaques (10) se composent de préférence d'un matériau métallique, en particulier d'aluminium, où les plaques sont recouvertes, de préférence sur au moins un côté, d'un matériau d'apport auxiliaire de brasage.
  8. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les perçages associés aux conduites d'amenée sont ovales, elliptiques ou rectangulaires.
  9. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que deux plaques (10) différentes l'une de l'autre par le profil ondulé (12) sont utilisées de façon alternée, où les profils ondulés (12) se différencient au moins par l'une des caractéristiques parmi celles concernant la longueur de branche (15), l'angle de branche (13) et la profondeur de profil.
  10. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le profil ondulé (12) de l'un des côtés de la plaque (10) se différencie du profil ondulé (12) de l'autre côté de la plaque (10), au moins par l'une des caractéristiques parmi celles concernant la longueur de branche (15), l'angle de branche (13) et la profondeur de profil.
  11. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le profil ondulé de plaques contiguës est identique l'un par rapport à l'autre.
  12. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'échangeur de chaleur est formé par une pile (21) de plaques (10), où les plaques (10) se correspondent l'une l'autre et sont disposées en étant tournées, de façon alternée, de 180° l'une par rapport à l'autre.
  13. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les plaques (10) présentent un bord coudé (17), où les bords (17) de plaques contiguës (10) sont en appui les uns contre les autres et sont assemblés les uns aux autres de préférence par brasage fort.
  14. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le bord coudé (17) recouvre plusieurs plaques, en particulier jusqu'à cinq plaques (10).
  15. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le profil ondulé (12) s'étend jusque dans le bord (17), en particulier au-delà du bord (17).
  16. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que, entre l'extrémité du profil ondulé et le bord, est configurée une partie de pliage, sans profil, dont la largeur est inférieure à 2 mm, et est déterminée de préférence de manière telle, que lors du brasage fort des plaques, de la brasure soit ajoutée à la zone de pliage, dans des parties de crêtes d'ondulations, de manière telle qu'une circulation d'un milieu soit réduite ou pratiquement empêchée dans la partie de pliage.
  17. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une plaque terminale (24), en particulier sans profil au moins extérieurement, est associée à au moins un côté frontal de l'échangeur de chaleur, plaque terminale qui présente de préférence des points de raccordement (25) pour un premier et un deuxième milieu, points de raccordement qui débouchent dans des conduites de raccordement et sont disposés en étant alignés par rapport aux perçages (18).
  18. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le diamètre hydraulique (hD) présente, dans la direction principale d'étendue (D), une variation au maximum de 25 %, en particulier au maximum de 15 %, en particulier au maximum de 10 % par rapport à une valeur moyenne.
  19. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que le diamètre hydraulique (hD) présente une valeur moyenne comprise entre 1 mm et 4 mm, où ledit diamètre, dans le cas de milieux liquides, est compris de préférence entre 1 mm et 2 mm et de préférence de 1,4 mm, et où, dans le cas de milieux gazeux, est de préférence de 3 mm.
  20. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les points de contact, entre deux plaques contiguës l'une à l'autre, sont répartis de façon uniforme sur la surface des plaques.
  21. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les points de contact présentent, entre deux plaques contiguës l'une à l'autre, une densité de surface de 4 à 7 par cm2, en particulier de 5 à 6 par cm2.
  22. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une transition de phase d'un milieu se produit dans des espaces intermédiaires de plaques.
  23. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que la position de montage de l'échangeur de chaleur est déterminée, par le fait que la distribution transversale du milieu, dans les espaces intermédiaires de plaques, est aidée par la gravitation.
EP04763632.9A 2003-08-01 2004-07-29 Echangeur de chaleur et procede de fabrication dudit echangeur Expired - Lifetime EP1654508B2 (fr)

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DE10336033 2003-08-01
PCT/EP2004/008542 WO2005012820A1 (fr) 2003-08-01 2004-07-29 Echangeur de chaleur et procede de fabrication dudit echangeur

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US (1) US8061416B2 (fr)
EP (1) EP1654508B2 (fr)
JP (1) JP2007500836A (fr)
CN (1) CN1833153B (fr)
BR (1) BRPI0413194B1 (fr)
DE (1) DE102004036951A1 (fr)
WO (1) WO2005012820A1 (fr)

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Also Published As

Publication number Publication date
EP1654508B1 (fr) 2016-10-19
JP2007500836A (ja) 2007-01-18
DE102004036951A1 (de) 2005-05-25
EP1654508A1 (fr) 2006-05-10
US8061416B2 (en) 2011-11-22
CN1833153B (zh) 2012-04-04
US20070107890A1 (en) 2007-05-17
CN1833153A (zh) 2006-09-13
WO2005012820A1 (fr) 2005-02-10
BRPI0413194A (pt) 2006-10-03
BRPI0413194B1 (pt) 2019-04-30

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