EP1725824A1 - Echangeur thermique a empilement de disques - Google Patents

Echangeur thermique a empilement de disques

Info

Publication number
EP1725824A1
EP1725824A1 EP05715746A EP05715746A EP1725824A1 EP 1725824 A1 EP1725824 A1 EP 1725824A1 EP 05715746 A EP05715746 A EP 05715746A EP 05715746 A EP05715746 A EP 05715746A EP 1725824 A1 EP1725824 A1 EP 1725824A1
Authority
EP
European Patent Office
Prior art keywords
stacked
heat exchanger
plate
exchanger according
plate heat
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.)
Granted
Application number
EP05715746A
Other languages
German (de)
English (en)
Other versions
EP1725824B1 (fr
Inventor
Jens Richter
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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 Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1725824A1 publication Critical patent/EP1725824A1/fr
Application granted granted Critical
Publication of EP1725824B1 publication Critical patent/EP1725824B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • 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
    • 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
    • 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
    • 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
    • F28F9/0234—Header boxes; End plates having a second heat exchanger disposed there within, e.g. oil cooler
    • 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

Definitions

  • the invention relates to a stacked-plate heat exchanger, in particular an intank oil cooler, for motor vehicles, with a plurality of stacked and connected, in particular soldered, elongated plates, each of which is composed of two identical plate halves rotated by 180 ° to one another and a cavity enclose for the passage of a medium to be cooled, such as oil, in the longitudinal direction of the disks.
  • a medium to be cooled such as oil
  • a disc heat exchanger is known with stacked and soldered discs, which are composed of two identical disc halves rotated by 180 ° and enclose a cavity for conducting a medium to be cooled.
  • the disk halves are provided with a pronounced edge for soldering the disk halves to a disk and with connection surfaces for soldering the disks to one another.
  • the disc halves are provided with frustoconical shapes on the inner and outer surfaces.
  • the disc halves are designed mirror-symmetrical to their transverse and / or longitudinal axis.
  • the frustoconical shapes are arranged like a chessboard between the connection surfaces. Positive expressions alternate with negative expressions.
  • the positive forms and the negative forms are similar to nubs.
  • the disc halves When assembled, the disc halves enclose a cavity that is surrounded by one Fluid, for example oil, is flowed through.
  • the knobs protruding into this cavity should ensure a good swirling of the oil and increase the strength as a result of their tie rod function.
  • the object of the invention is to provide a stacked-plate heat exchanger, in particular an intank oil cooler, for motor vehicles, with a plurality of stacked and connected, in particular soldered, elongated plates, each of which is composed of two identical plate halves rotated by 180 ° to one another and one Enclose a cavity for the passage of a medium to be cooled, such as oil, in the longitudinal direction of the disks, which is simple in construction and can be produced inexpensively.
  • the stacked disk heat exchanger according to the invention is nevertheless intended to ensure a good swirling of the medium to be cooled in the cavity formed between the disk halves.
  • the task is for a stacked-plate heat exchanger, in particular an intank oil cooler, for motor vehicles, with a plurality of stacked and connected, in particular soldered, elongated plates, which are each composed of two plate halves and have a cavity for carrying a medium to be cooled, such as Enclose oil in the longitudinal direction of the disks, solved in that each of the disk halves has a plurality of grooves that run from one long side to the opposite long side of the disk half.
  • the discs are also called flat tubes or plates.
  • the course of the grooves ensures the passage of coolant from one long side of the disc half to the opposite long side.
  • the Rijlen ensure a good swirling of the medium to be cooled.
  • a preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that the elongated plates are each composed of two identical plate halves rotated by 180 ° to one another. This considerably simplifies the manufacture of the stacked-plate heat exchanger according to the invention.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that the grooves run in a straight line from one long side to the opposite long side of the plate half. This ensures unimpeded passage of coolant from one long side of the pane half to the opposite long side.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that the grooves are pronounced on one side in each half of the plate.
  • the grooves are formed by straight, elongated, narrow depressions which are embossed on one side, for example in a sheet metal material. Since the grooves are only pronounced on one side, the manufacture of the disc halves is simplified.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that the grooves on the long sides are delimited by a peripheral edge.
  • the circumferential edge serves to connect two halves of the pane to one another, in particular to solder them. This seals the cavity between the two pane halves from the outside.
  • a plate is formed by two mutually abutting plate halves, the grooves of which are pronounced on the outside.
  • the grooves in the interior of the disk limit the flow path of the medium to be cooled.
  • An inlet for the medium to be cooled is preferably provided at one end of the disk and an outlet at the other end of the disk.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that two plates abut one another with their raised regions formed by the grooves and are connected to one another by a soldering process. Coolant, for example water, can pass between the raised areas from one long side to the opposite long side of the respective pane half.
  • the panes in the edge area of through holes are equipped with cup-shaped, raised areas, on which the panes are also soldered to one another.
  • Another preferred embodiment of the stacked-plate heat exchanger is characterized in that the grooves run at an angle of 35 ° to 55 °, in particular 45 °, to the longitudinal axis of the associated plate half.
  • the course of the grooves according to the invention also ensures that the coolant can flow in two disks from one long side to the opposite long side.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that the grooves of two mutually abutting plate halves are arranged at an angle of 70 ° to 110 °, in particular of 90 °, to one another. This will make for that too . cooling medium inside the discs created a flow path that has many changes of direction and vortex. This has the advantage that boundary layers that form in the cavity are repeatedly torn open during operation.
  • the angle of 90 ° results in an almost circular solder meniscus at the junction of the two grooves.
  • the angle is preferably 80 ° to 100 °.
  • the grooves have a depth of 0.8 to 1.5 mm, in particular 1.15 mm. This depth has proven to be particularly advantageous in the context of the present invention.
  • the grooves preferably have a depth of 0.5 mm to 1.5 mm.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that the grooves of one half of the plate are arranged parallel to one another at a distance of 3 to 5 mm, in particular 4 mm, from one another. This division has proven to be particularly advantageous in the context of the present invention.
  • the plate halves have a width of approximately 20 to 50 mm. This width has proven to be particularly advantageous in the context of the present invention. In the case of commercial vehicles, the pane halves preferably have a width of approximately 20 to 120 mm. A width of 70 to 80 mm, in particular of 76 mm, is particularly preferred.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that the hydraulic diameter has a value of 1.5 to 2.5 mm, in particular 1.8 mm. This value has proven to be particularly advantageous in the context of the present invention. ,
  • the hydraulic diameter between two adjacent disc halves along the main direction of flow of the medium to be cooled represents the ratio between the flowable channel cross section and the heat exchange area.
  • the hydraulic diameter is defined as four times the ratio of the area ratio to the area density.
  • the area ratio is determined as the ratio of the free channel cross section to the total face area of the channel between two adjacent disc halves.
  • the areal density is determined from the ratio between the heat transfer area and the block volume.
  • the hydraulic diameter should preferably be as constant as possible across the entire main flow direction of the medium to be cooled. stay steadfast. This achieves a uniform flow through the cavity between two disc halves.
  • Another preferred exemplary embodiment of the stacked heat exchanger is characterized in that the pulley halves are made of 'a metal material, in particular of aluminum or stainless steel, is formed. The disks are preferably joined together by brazing. Stainless steel is preferred for commercial vehicles.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that at least one side of the plate halves is coated with soldering aid material. The manufacturing process of the stacked-plate heat exchanger according to the invention can thereby be simplified.
  • the plate halves each have a pair of through holes as inflow lines and outflow lines.
  • the medium to be cooled passes through the through holes into the cavity between two disc halves forming a disc or a flat tube.
  • the discs can also be referred to as plates and the disc halves as plate halves.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that the edge region of the through holes is raised.
  • the edge region of the through holes is preferably raised as far as the grooves or shafts.
  • Two abutting raised edge regions of different disc halves seal the through holes and the cavity between two disc halves connected to the through holes from the environment through which coolant flows.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that in the edge region Through holes embossments are provided. The impressions serve to reinforce the disc halves in the area of the through holes.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that the impressions, viewed in section, are designed in a wave-like manner with wave crests and wave troughs in the inlet area.
  • the wave crests and wave troughs essentially create selective contacts between two adjacent disc halves.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that a plurality of plate halves in the inlet region are soldered to the adjacent plate halves in a substantially linear manner both on their inside and on their outside. As a result, the internal pressure resistance of the tubes, which are each made up of two disc halves, rises sharply.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that the impressions, viewed in plan view, run at least partially around the through-holes in a meandering manner. This increases the contact area between two disc halves.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that two plate halves are connected to one another in one piece by a bending edge running in the longitudinal direction or in the transverse direction in order to form a conduit device for the medium to be cooled. Since the two disc halves are already connected to each other in one piece at the bending edge, they only have to be soldered to one side. This increases the cross section through which the medium to be cooled flows. In addition, the number of individual parts required is reduced by half, since one part is required per line device.
  • the conduit device is formed by an elongated, in particular essentially rectangular, plate which is divided into two elongated halves by the bending edge and which are folded together.
  • the plate is preferably an embossed stamped part made of a metallic material that is simple and inexpensive to manufacture. When folded, the plate halves are congruent.
  • the plate has a peripheral edge which is raised in relation to the plate surface.
  • the plate is preferably stamped within the circumferential edge, the depth of the stamped surface being half the clear width of the line device.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that the peripheral edge is interrupted at the intersection with the bending edge. In the area of the bending edge, the plate has the same depth over the entire length of the bending edge. This prevents undesirable damage to the plate material in the area of the bending edge when folding.
  • Another preferred exemplary embodiment of the stacked-plate heat exchanger is characterized in that the two plate halves lie against one another with the circumferential edge in the folded state.
  • the plate halves are preferably soldered to one another on the peripheral edge.
  • the above-mentioned object is achieved in that a stacked-plate heat exchanger described above is installed in the water box.
  • Figure 1 is a perspective view of a disc half
  • Figure 2 shows an end of the disc half of Figure 1 in the bottom view
  • FIG. 3 shows the view of a section along the line III-III in FIG. 2;
  • Figure 4 is a perspective view of two disc halves
  • FIG. 5 shows an enlarged detail from FIG. 4
  • FIG. 6 shows a perspective illustration of seven disks which are assembled to form a stacked disk heat exchanger according to the invention
  • Figure 7 is an enlarged perspective view of an end plate of the stacked plate heat exchanger shown in Figure 6;
  • FIG. 8 shows the view of a cross section through one end of the stacked-plate heat exchanger shown in FIG. 6;
  • Figure 9 shows an end of the stacked plate heat exchanger shown in Figure 6 in side view
  • Figure 10 is a perspective view of a water tank with a built-in stacked plate heat exchanger
  • FIG. 11 shows a cooler with a built-in water tank, as shown in FIG. 10;
  • FIG. 12 shows a representation of the solder menisci in the channel section;
  • FIG. 13 shows a top view of almost circular solder menisci
  • FIG. 14 is a top view of a stacked-plate heat exchanger according to a further exemplary embodiment of the invention.
  • FIG. 15 is a side view of the stacked-plate heat exchanger from FIG. 14;
  • FIG. 16 shows the view of a section along the line XVI-XVI in FIG. 14;
  • FIG. 17 shows the view of a section along the line XVII-XVII in FIG. 14;
  • FIG. 18 shows the view of a section along the line XVIII-XVIII in FIG. 14;
  • Figure 19 is an enlarged view of detail XIX of Figure 14;
  • Figure 20 shows a line device according to the invention in the opened state in plan view
  • FIG. 21 shows the line device from FIG. 20 in the half-folded state
  • FIG. 22 shows a stacked-plate heat exchanger with a closed line device, as shown in FIGS. 20 and 21, in the closed state in a top view;
  • Figure 23 shows the stacked disc heat exchanger from Figure 22 in side view
  • FIG. 24 shows the view of a section along the line XXIV-XXIV in FIG. 22.
  • a disc half 1 is shown in perspective.
  • the disc half 1 has the shape of an elongated plate made of aluminum sheet with two straight longitudinal sides 2 and 3, which are arranged parallel to each other. At its ends 4 and 5, the disc half 1 is rounded off in a semicircle. Through holes 8 and 9 are provided in the ends 4 and 5.
  • the edge regions 10, 11 of the through holes 8, 9 are recessed so that the edge regions 10, 11 are raised on the underside of the pane half 1.
  • a plurality of grooves 12 are formed in the disk half 1 between the through holes 8 and 9.
  • the grooves 12 run in a straight line from one long side 2 to the opposite long side 3 of the disc half 1.
  • the grooves have the shape of elongated depressions which are raised on the underside of the disc half 1.
  • the grooves can also not run in a straight line, for example in the form of waves or zigzags.
  • the end 4 of the disc half 1 of Figure 1 is shown in the bottom view.
  • the edge area 10 and ten grooves 21 to 30 rise from the plane of the drawing.
  • the ends of the grooves 21 to 30 are rounded towards the long sides 2, 3.
  • the longitudinal axis of the disc half 1 is designated 31.
  • the grooves 21 to 30 are arranged at an angle ⁇ of 45 ° to the longitudinal axis 31.
  • the disk half 42 has exactly the same shape as the disk half 1. However, the disk half 42 is rotated by 180 ° with respect to the disk half 1. An end 44 with a through hole 48, the edge region 50 of which rises from the plane of the drawing, is arranged above the through hole 8 of the end 4 of the pane half 1, the cup-shaped edge region 10 of the through hole 8 rising into the plane of the drawing. Grooves 52 are formed in the disk half 42 and rise out of the plane of the drawing. The grooves 52 are arranged at an angle ⁇ of 90 ° to the grooves 12, which rise into the plane of the drawing. The two disc halves 1 and 42 are soldered together to form a disc or a flat tube at the contact points of the grooves and in the edge region 2 and 3.
  • a plurality of disks 60 are soldered to one another in FIG.
  • the through holes of the disks 60 are closed by end disks 61, 62.
  • connecting pieces 67, 68 are placed on the upper side of the disks 60.
  • the medium to be cooled can be introduced into the interior of the panes 60 through one of the connecting pieces 67, 68.
  • the medium to be cooled can emerge from the disks 60 from the other connecting piece 68, 67.
  • the lens 61 is shown enlarged perspective.
  • the cover disk 61 has the shape of a circular disk 64 which has a circular, central elevation 65.
  • the outer diameter of the circular elevation 65 is matched to the inner diameter of the associated through hole of the respective disk.
  • FIGS. 8 and 9 show that the stacked-plate heat exchanger shown in perspective in FIG. 6 comprises seven plates 71 to 77, which are stacked one above the other.
  • a plurality of substantially zigzag-shaped flow paths for the medium to be cooled are formed in the interior of the disks 71 to 77, which flow between the disks 71 to 77 in a straight line through the recessed areas between two grooves from one side to the opposite side of the corresponding half of the disc run.
  • FIG. 10 shows a water box 78 in which the stacked-plate heat exchanger shown in FIG. 6 is installed.
  • the disks 60 are arranged within the water box 78.
  • the end connections 67, 68 protrude from the water box 78.
  • the water tank 78 from FIG. 10 is attached to one side of a cooling network 79.
  • Another water tank 80 is attached to the other side of the cooling network 79.
  • the two water boxes 78 and 80 and the cooling network 79 together form a coolant cooler 81 of a motor vehicle (not shown).
  • the profiling of the disc halves 1 and 42 is designed so that the
  • the leg angle of the profiling is 45 ° to the main flow direction of the medium to be cooled.
  • the hydraulic diameter is 1.8 mm.
  • the embossing angle is in a range between 20 ° and 60 ° to the main flow direction.
  • the hydraulic diameter can vary between 1.5 mm and 2.5 mm.
  • the large area in the entry and exit area enables a tight pane connection without the need to use additional components.
  • the disc halves have horizontal soldering surfaces, which ensures sufficient flow of coolant on the outside of the cooler.
  • the disc halves are preferably slightly angled at their peripheral edge. This improves the flatness of the washer when unsoldered.
  • the bend angle is between 5 ° and 20 °, preferably 10 °.
  • the disc halves are made of aluminum and are connected to each other by a wheel soldering process.
  • FIG. 12 it can be seen that two disk halves are connected to one another by soldering menisci 101, 102 and 103, 104.
  • FIG. 13 it can be seen that the solder menisci 101 to 104 are almost circular in plan view.
  • FIG. 14 shows a plate half 1 of a stacked plate heat exchanger according to the invention in accordance with a further exemplary embodiment. The same reference numerals are used to designate the same parts as in the embodiment shown in FIG. 1. To avoid repetition, reference is made to the previous description of FIG. 1. Only the differences between the exemplary embodiments are discussed below.
  • the edge regions 110, 111 of the through holes 8, 9 are provided with embossments.
  • the edge region 111 at the end 5 of the pane half 1 has meandering impressions 115 and 116 which are connected by a connecting bead 117.
  • the edge region 110 at the end 4 of the pane half 1 has meandering impressions 118 and 119 which are connected to one another by a connecting bead 120.
  • Two disk halves 1, as shown in FIG. 14, are, as described above, to form a disk or a flat tube, which is also referred to as a line device, at the contact points of the grooves 12 and in the edge regions 2 and 3 as well the impressions 118, 119 soldered together.
  • FIG. 15 shows a side view of a radiator block which comprises a plurality of flat tubes stacked one above the other.
  • FIG. 16 shows the view of a section along the line XVI-XVl in FIG. 14.
  • various flat tubes of a radiator block are stacked in a row in the area of the meandering impressions 115, 116 and on the impressions 118, 119.
  • FIG. 17 shows the view of a section along the line XVII-XVII in FIG. 14.
  • the sectional view shows that the number of essentially linear contact areas is increased by the meandering impressions 116.
  • the meandering impressions 116 are also referred to as reinforcing beads.
  • Embossments at the end of the plate are soldered to each other both on the inside and on the outside of the stacked plate heat exchanger.
  • FIG. 18 shows the view of a section along the line XVIII-XVIII in FIG. 14. Here you can see how the embossments 119 on the plate end 4 are soldered to one another both on the inside and on the outside of the stacked plate heat exchanger.
  • FIG. 19 shows an enlarged illustration of the detail XIX from FIG. 14.
  • the shape of the embossments 118, 119 is designed in such a way that disks stacked one above the other are soldered to one another in a linear fashion both on the inside and on the outside. As a result, the internal pressure resistance of a tube formed from two disc halves increases sharply.
  • the disc connections are shown meandering in Figure 19.
  • FIG. 20 shows a line device 140, which is also referred to as a flat tube or a short tube, in the opened state.
  • the flat tube 140 is formed by a plate 142 which essentially has the shape of a rectangle, the corners of which are rounded.
  • the plate 142 is a stamped part made of aluminum sheet, which has a bending edge 143, through which the plate 142 is divided in the longitudinal direction into two halves 145, 146 of equal size, which are also referred to as disc halves. Apart from their one-piece design, the two disc halves 145, 146 correspond to the disc halves of the previous exemplary embodiments.
  • the plate 142 is delimited on the outside by a circumferential edge 148 which serves to solder the two plate halves 145, 146 to one another in the folded or folded state.
  • a circumferential edge 148 which serves to solder the two plate halves 145, 146 to one another in the folded or folded state.
  • the plate halves 145, 146 are provided with embossed grooves, as described above.
  • the pipe 140 is shown in a top view in the closed state.
  • the tube 140 is the top flat tube of a stacked plate heat exchanger with several stacked flat tubes.
  • FIG. 23 shows a side view of the stacked-plate heat exchanger from FIG. 22.
  • the side view shows that the stacked-plate heat exchanger comprises, in addition to the flat tube 140, six further flat tubes 150 to 155, which are soldered to one another in a stacked manner.
  • FIG. 24 shows the view of a section along the line XXIV-XXIV in FIG. 22.
  • the sectional view shows that the stacked-plate heat exchanger is made up of folded flat tubes .140, 150 to 155.
  • the one-piece design of the flat tubes reduces the number of parts required for the construction of the stacked-plate heat exchanger by half.
  • the folded flat tubes have the advantage that the length of the sealing seam is reduced by almost half.

Landscapes

  • 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)

Abstract

La présente invention concerne un échangeur thermique à empilement de disques, en particulier un refroidisseur d'huile intra-réservoir, qui est intégré à une enceinte d'agent de refroidissement d'un dispositif de refroidissement à agent de refroidissement, et destiné à des véhicules automobiles, ledit échangeur thermique comprenant plusieurs disques longitudinaux (71-77) qui sont empilés les uns sur les autres, et reliés entre eux, en particulier soudés, et qui sont composés respectivement de deux moitiés de disque, et entourent, dans la direction longitudinale des disques, une cavité destinée à l'acheminement d'une substance à refroidir telle que de l'huile. Pour permettre une réalisation économique d'un échangeur thermique à empilement de disques, chacune des moitiés de disques présente une pluralité de nervures qui s'étendent d'un côté longitudinal au côté longitudinal opposé de la moitié de disque.
EP05715746.3A 2004-03-11 2005-03-04 Echangeur thermique a empilement de disques Not-in-force EP1725824B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004012329 2004-03-11
PCT/EP2005/002317 WO2005088223A1 (fr) 2004-03-11 2005-03-04 Echangeur thermique a empilement de disques

Publications (2)

Publication Number Publication Date
EP1725824A1 true EP1725824A1 (fr) 2006-11-29
EP1725824B1 EP1725824B1 (fr) 2015-12-02

Family

ID=34961498

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05715746.3A Not-in-force EP1725824B1 (fr) 2004-03-11 2005-03-04 Echangeur thermique a empilement de disques

Country Status (5)

Country Link
EP (1) EP1725824B1 (fr)
JP (1) JP4944009B2 (fr)
KR (1) KR20060130207A (fr)
CN (1) CN100516760C (fr)
WO (1) WO2005088223A1 (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE531472C2 (sv) * 2005-12-22 2009-04-14 Alfa Laval Corp Ab Värmeväxlare med värmeöverföringsplatta med jämn lastfördelning på kontaktpunkter vid portområden
KR101078554B1 (ko) * 2009-02-03 2011-11-01 서진욱 테두리가 보강된 디스크타입의 열교환기
KR100950689B1 (ko) * 2009-04-16 2010-03-31 한국델파이주식회사 플레이트 열교환기
KR101148925B1 (ko) * 2009-07-27 2012-05-23 한국델파이주식회사 플레이트 열교환기
KR100967181B1 (ko) * 2009-07-27 2010-07-05 한국델파이주식회사 플레이트 열교환기
WO2011013950A2 (fr) * 2009-07-27 2011-02-03 한국델파이주식회사 Echangeur de chaleur à plaques
DE102010063074B3 (de) * 2010-12-14 2012-04-12 INSTITUT FüR MIKROTECHNIK MAINZ GMBH Mikrofluidisches Bauteil, Reaktor aus mehreren solchen Bauteilen und Verfahren zu deren Herstellung
JP2012141096A (ja) * 2010-12-28 2012-07-26 Mitsubishi Heavy Ind Ltd 温水ヒータの製造方法、これにより製造された温水ヒータ
CN102647884B (zh) * 2011-02-17 2015-03-18 北汽福田汽车股份有限公司 散热器及其散热水道***结构
KR101405186B1 (ko) * 2012-10-26 2014-06-10 현대자동차 주식회사 차량용 열교환기
CN104755869B (zh) * 2012-10-31 2017-03-08 达纳加拿大公司 具有单块板设计的堆叠板式换热器
US9057564B2 (en) * 2012-12-17 2015-06-16 Baltimore Aircoil Company, Inc. Cooling tower with indirect heat exchanger
JP6192564B2 (ja) * 2014-02-18 2017-09-06 日新製鋼株式会社 プレート式熱交換器およびその製造方法
CN103791759B (zh) * 2014-03-07 2016-03-30 丹佛斯微通道换热器（嘉兴）有限公司 用于板式换热器的热交换板以及具有该热交换板的板式换热器
CN112781426B (zh) * 2019-11-08 2023-03-28 丹佛斯有限公司 用于板式换热器的换热板和板式换热器

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1990007091A1 (fr) * 1988-12-12 1990-06-28 Vulcan Australia Limited Echangeur thermique
GB8910966D0 (en) * 1989-05-12 1989-06-28 Du Pont Canada Panel heat exchangers formed from thermoplastic polymers
CA2150437C (fr) * 1995-05-29 1999-06-08 Alex S. Cheong Echangeur a plaques muni d'un passage onduleux ameliore
SE9601438D0 (sv) * 1996-04-16 1996-04-16 Tetra Laval Holdings & Finance Plattvärmeväxlare
FR2795165B1 (fr) * 1999-06-21 2001-09-07 Valeo Thermique Moteur Sa Echangeur de chaleur a plaques, en particulier refroidisseur d'huile pour vehicule automobile
US20030131979A1 (en) * 2001-12-19 2003-07-17 Kim Hyeong-Ki Oil cooler
CA2389119A1 (fr) * 2002-06-04 2003-12-04 Christopher R. Shore Echangeur thermique a ailettes a plaques laterales
JP2004205057A (ja) * 2002-12-20 2004-07-22 Toyo Radiator Co Ltd プレート型熱交換器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005088223A1 *

Also Published As

Publication number Publication date
CN100516760C (zh) 2009-07-22
WO2005088223A8 (fr) 2007-02-22
CN1930440A (zh) 2007-03-14
JP4944009B2 (ja) 2012-05-30
EP1725824B1 (fr) 2015-12-02
WO2005088223A1 (fr) 2005-09-22
JP2007527984A (ja) 2007-10-04
KR20060130207A (ko) 2006-12-18

Similar Documents

Publication Publication Date Title
EP1725824B1 (fr) Echangeur thermique a empilement de disques
EP1654508B1 (fr) Echangeur de chaleur et procede de fabrication dudit echangeur
DE60117693T2 (de) Wärmetauscher, insbesondere als Kraftstoffkühler bei Brennkraftmaschinen von Kraftfahrzeugen
DE60319986T2 (de) Plattenwärmetauscher
WO2005071342A1 (fr) Echangeur de chaleur, notamment radiateur d'huile/de liquide de refroidissement
DE60009282T2 (de) Wärmetauscher mit genopptem bypasskanal
DE102007049665A1 (de) Wärmeaustauscher
DE9406197U1 (de) Wärmetauscher zum Kühlen von Abgas eines Kraftfahrzeugmotors
DE10220532A1 (de) Wärmetauscher
DE10348803A1 (de) Plattenwärmetauscher
EP1842020B1 (fr) Echangeur thermique a empilement de plaques
DE19909881A1 (de) Wärmeübertrager in Kreuzstrom-Bauweise
DE69411677T2 (de) Lamellenwärmetauscher, insbesondere Ölkühler für Kraftfahrzeug
DE3440489A1 (de) Kuehler, insbesondere fuer die kuehlanlage eines verbrennungsmotors eines kraftfahrzeuges
DE19728247A1 (de) Flache Röhre für einen Wärmetauscher
DE10152363A1 (de) Gehäuseloser Plattenwärmetauscher
DE3142028C2 (fr)
DE202008013351U1 (de) Wärmeaustauschernetz und damit ausgerüsteter Wärmeaustauscher
EP0444595B1 (fr) Echangeur de chaleur, en particulier refroidisseur d'huile pour véhicule automobile
DE3728303A1 (de) Waermetauscher mit einer rippen-rohranordnung
WO2006013075A1 (fr) Element intercalaire de turbulence monobloc
DE102004007510A1 (de) Wärmeübertrager, insbesondere Ölkühler für Kraftfahrzeuge
DE19605340C2 (de) Wärmeübertrager und Verfahren zu seiner Herstellung
DE4437877C2 (de) Wärmetauscher, insbesondere Ölkühler
DE60009284T2 (de) Rohr zum Transport eines Kühlmittels durch einen Wärmetauscher

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20061011

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

RIN1 Information on inventor provided before grant (corrected)

Inventor name: RICHTER, JENS

DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20100913

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MAHLE BEHR GMBH & CO. KG

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150625

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

RIN1 Information on inventor provided before grant (corrected)

Inventor name: RICHTER, JENS

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 763818

Country of ref document: AT

Kind code of ref document: T

Effective date: 20151215

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502005015027

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20160302

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160303

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160404

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160402

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160331

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502005015027

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160304

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26N No opposition filed

Effective date: 20160905

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20160304

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160304

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160331

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160331

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160304

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 763818

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160304

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160304

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20050304

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20180319

Year of fee payment: 14

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151202

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20180329

Year of fee payment: 14

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005015027

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191001

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190331