EP0450425B1 - Agencement pour échangeur de chaleur - Google Patents

Agencement pour échangeur de chaleur Download PDF

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Publication number
EP0450425B1
EP0450425B1 EP19910104510 EP91104510A EP0450425B1 EP 0450425 B1 EP0450425 B1 EP 0450425B1 EP 19910104510 EP19910104510 EP 19910104510 EP 91104510 A EP91104510 A EP 91104510A EP 0450425 B1 EP0450425 B1 EP 0450425B1
Authority
EP
European Patent Office
Prior art keywords
heat
heat exchanger
heat exchangers
exchanger
air
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.)
Expired - Lifetime
Application number
EP19910104510
Other languages
German (de)
English (en)
Other versions
EP0450425A2 (fr
EP0450425A3 (fr
Inventor
Dieter Roschinski
Michael Klocke
Hans Weitzenbürger
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Kloeckner Humboldt Deutz AG
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
Priority claimed from DE19904009726 external-priority patent/DE4009726A1/de
Priority claimed from DE19904033897 external-priority patent/DE4033897A1/de
Application filed by Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Priority to DE59103074T priority Critical patent/DE59103074D1/de
Publication of EP0450425A2 publication Critical patent/EP0450425A2/fr
Publication of EP0450425A3 publication Critical patent/EP0450425A3/fr
Application granted granted Critical
Publication of EP0450425B1 publication Critical patent/EP0450425B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0452—Combination of units extending one behind the other with units extending one beside or one above the other

Definitions

  • the invention relates to a heat exchanger arrangement with at least two heat exchangers, which are acted upon by cooling air from a common fan.
  • the coolant heat exchanger is usually arranged in front of the internal combustion engine. There is a fan between the internal combustion engine and the coolant heat exchanger, which conveys the cooling air through the heat exchanger. In order to achieve a uniform loading of the heat exchanger and at the same time a small distance between the heat exchanger and fan, a square active surface of the heat exchanger is usually aimed for.
  • Such heat exchangers are e.g. known from the document US-A-2 264 820.
  • Additional units are often driven by internal combustion engines, which require a considerable cooling capacity for the working medium of the additional unit.
  • the additional heat exchanger required is often larger than the coolant heat exchanger of the internal combustion engine. It is difficult to apply cooling air evenly to both heat exchangers and at the same time to accommodate them at a short distance from the fan.
  • the invention has for its object to provide a heat exchanger fan system with at least two heat exchangers and a fan that requires as little space as possible.
  • the object is achieved by the characterizing features of claim 1.
  • the standard heat exchanger for the coolant of the internal combustion engine has a simple square or rectangular shape, while the additional heat exchanger has an L-shape. This is adapted in size to the heat quantities to be dissipated and realizes the overall square shape of the active surfaces of the heat exchangers. Due to the arrangement according to the invention, even when the fan is at a small distance from the plane of the heat exchanger, the active surfaces of the heat exchanger are uniformly acted on, since these are optimally coated by the fan because of their approximately square shape.
  • a pressure fan also offers advantages, e.g. B. a lower fan power because of the lower volume of the cold air to be conveyed.
  • advantages of the invention apply to both types of fans.
  • An advantageous development of the invention has the effect that, in an internal combustion engine with a constant amount of cooling heat and additional units with different amounts of cooling heat, a coolant heat exchanger of constant dimensions with different sizes of heat exchanger for the working medium can be combined to the optimal combination according to the invention.
  • the flow resistances on the cooling air side of both heat exchangers are designed approximately the same, whereby a uniform cooling air distribution is also promoted.
  • An advantageous development of the invention achieves the same effect even in charge air-cooled engines in which the charge air cooler is arranged upstream of the coolant heat exchanger.
  • This location of the charge air cooler also has the effect that only the cooling air of the first heat exchanger is preheated, while that of the second heat exchanger is not preheated, so that its dimensions do not have to be increased.
  • the effectiveness of the fan is increased by an advantageous embodiment of the invention.
  • the cooling air duct prevents the sucking in or blowing off of external air and thus increases the efficiency and noise level of the fan. If fan efficiency and fan noise play no role in comparison to the purchase costs of the cooling air duct, the cooling air duct can also be omitted.
  • the fan is replaced by a blower with a stator, which enables the use of compact high-performance heat exchangers with increased flow resistance due to the increased cooling air pressure caused thereby.
  • a further cost reduction is achieved by an advantageous development of the invention.
  • the same end box blanks mean only one mold and only one raw part store.
  • the least amount of processing and assembly work and the smallest risk of leakage on the one hand, in which only the required minimum processing of the various end boxes is carried out and the complete equality of all finished end boxes with correspondingly simplified storage, on the other hand, but increased processing and assembly costs and increased Leakage risk, since in this case all holes that are not required but are drilled must be closed.
  • two individual heat exchangers with identical active surfaces can also be used.
  • the equality of the components is contrasted here by the incomplete use of the square area as a disadvantage, whereby the unused area must be covered.
  • the first heat exchanger 1 has a rectangular-shaped active surface, which is supplemented by the second heat exchanger 2 due to its coordinated L-shape to a square shape of the entire active surface.
  • the first heat exchanger 1 is used for recooling the cooling medium of the internal combustion engine
  • the second heat exchanger 2 is used for recooling the working medium of the additional equipment or units of the internal combustion engine.
  • Both heat exchangers have heat exchanger boxes 14, 14 ', 14 ⁇ , 14 ′′′, 14 ⁇ ⁇ , which are used for even distribution and for collecting the respective cooling medium.
  • the arrangement of the charge air cooler 12 is shown in FIG. This is arranged upstream of the first heat exchanger 1 and has the same effective area as this. It does heat the cooling air of the first heat exchanger 1 slightly. However, this has less of an impact on the cooling medium of the first heat exchanger 1 — usually cooling water — in contrast to the coolant of the second — generally hydraulic oil — because of the higher temperature level of the cooling water.
  • the resistance of the cooling air in the two or three heat exchangers is adjusted so that it is constant over the entire surface of the heat exchanger and thus causes a uniform flow of cooling air.
  • the fan 9 is designed as a suction fan. It is located a short distance behind the heat exchangers in the flow direction. Its diameter corresponds to the inner circle of the square area of the active surfaces of the heat exchangers. Between heat exchangers 1, 2, 12 and the fan 9, a cooling air duct 13 is arranged. It serves to guide the cooling air and prevents the fan 9 from sucking in false air. For the same reason, the first and second heat exchangers are joined together at a short distance. The resulting high efficiency of the heat exchanger fan system also lowers the noise level of the fan 9.
  • the arrangement of the heat exchangers according to the invention offers the advantage of uniform application to all active surfaces of the heat exchangers despite the small axial length due to the possible small fan spacing. In addition, heating of the cooling air of the second heat exchanger 2 is avoided, which keeps its dimensions as small as possible.
  • the heat exchanger arrangement according to FIG. 3 consists of a first heat exchanger 1 and a second heat exchanger 2.
  • the associated fan 9 is indicated in FIGS. 3 and 4 by a fan circuit.
  • the active surfaces of the heat exchangers 1, 2 form approximately a square, to which the fan circuit is inscribed.
  • the second heat exchanger 2 consists of two individual heat exchangers 3, 3a, 3b, 3c, 3d, which are arranged in an L-shape and surround the first heat exchanger 1 in half and add a square.
  • the second heat exchanger 2 is used, for example, to cool hydraulic oil.
  • the individual heat exchangers 3, 3a, 3b, 3c, 3d consist of a rectangular active surface 10, 10 ', which is delimited on two opposite sides by two end boxes 4, 4', 4 ⁇ .
  • the active surfaces 10, 10 ', the cooling liquid is supplied or discharged via the end boxes 4, 4', 4 ⁇ .
  • Each end box 4, 4 ', 4 ⁇ is made by different processing from the same blank.
  • Each end box 4, 4 ', 4 ⁇ has an end wall 7 and two end walls 8, 8', the outer surfaces of which intersect in the edges 6, 6 '.
  • a bore 5 is made either in the end wall 7 or in the end wall 8, which serves for the inlet or outlet of the cooling liquid.
  • the holes 5 have the same distance from the edge 6 and are made in the middle of the respective end wall 7 or end wall 8.
  • the end boxes 4, 4 ', 4 ⁇ are attached to the active surfaces 10, 10' so that their bores are diagonally opposite. As a result, a uniform distribution of the cooling liquid on the active surfaces 10, 10 'is achieved.
  • the individual heat exchangers 3, 3a, 3b, 3c, 3d touch each other with the end wall 7 and the end wall 8 of an end box 4, 4 ', 4 ⁇ . They are screwed together at the point of contact.
  • FIG. 3 shows a heat exchanger 2, the individual heat exchangers 3a, 3c of which belong to separate circuits.
  • the individual heat exchangers 3a, 3c are screwed together, but have separate coolant inflows and outflows.
  • FIG. 4 shows a heat exchanger 2, the individual heat exchangers 3, 3b, 3d of which are in flow connection via bores 5 at the contact point and thereby form a cooling unit which belongs to a single-circuit cooling system.
  • the contact surfaces are generally machined and provided with a seal 11 in the single-circuit cooling system.
  • the heat exchanger arrangement according to FIGS. 3 and 4 represents a compact and flexible solution in which low production costs are achieved by using as many standard and identical components as possible.

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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)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Claims (9)

  1. Agencement pour échangeur de chaleur avec au moins deux échangeurs de chaleur (1, 2) qui sont soumis à de l'air frais au moyen d'un ventilateur (9) commun, les échangeurs (1, 2) sont disposés dans un plan et se touchent sans vide, on choisit les dimensions et la forme de chaque échangeur de chaleur (1, 2) pour que les faces frontales des échangeurs de chaleur (1, 2) présentent en fait une surface de projection carrée, on prévoit le premier échangeur de chaleur (1) pour le liquide de refroidissement d'un moteur thermique, caractérisé en ce que le deuxième échangeur de chaleur (2) est prévu pour le liquide d'entraînement de matériels auxiliaires qui sont entraînés par le moteur thermique et que les dimensions du premier échangeur de chaleur (1) sont constantes, on choisit indifféremment les dimensions du deuxième échangeur de chaleur (2) en fonction de la puissance de refroidissement nécessaire, le premier échangeur de chaleur (1) présente une surface frontale carrée ou rectangulaire, et le deuxième échangeur de chaleur (2) une surface frontale en L.
  2. Agencement pour échangeur de chaleur selon la revendication 1, caractérisé en ce que le deuxième échangeur de chaleur (2) présente deux échangeurs de chaleur individuels (3, 3a, 3b, 3c, 3d), qui forment ensemble un L, chacun des échangeurs de chaleur individuels (3, 3a, 3b, 3c, 3d) forme une patte du L.
  3. Agencement pour échangeur de chaleur selon la revendication 2, caractérisé en ce que les échangeurs de chaleur individuels (3, 3a, 3b, 3c, 3d) présentent chacun deux caisses terminales (4, 4′) qui sont identiques du point de vue de leur usinage mécanique.
  4. Agencement d'échangeur de chaleur selon l'une des revendications 2 ou 3, caractérisé en ce que les surfaces frontales de chaque échangeur de chaleur (3, 3a, 3b, 3c, 3d) sont de forme rectangulaire et présentent au moins la même largeur.
  5. Agencement d'échangeur de chaleur selon l'une des revendications précédentes, avec des caisses terminales (4, 4′) qui présentent chacune une paroi terminale (7) ainsi que deux parois frontales (8, 8′), les parois terminales (7) et les parois frontales (8, 8′) se coupent en deux bords (6, 6′), caractérisé en ce que dans le domaine de bord (6) de chaque caisse terminale (4, 4′), on prévoit un espace dans la paroi terminale (7) et dans la paroi frontale (8) pour un alésage (5), les alésages prévus (5) ayant la même distance au bord (6) et aux bords latéraux de la paroi terminale (7) et de la paroi frontale (8), et que les caisses terminales (4, 4′) de chaque échangeur thermique (3, 3a, 3b, 3c, 3d) sont disposées de telle sorte que leurs bords (6) sont diagonalement opposés.
  6. Agencement d'échangeurs de chaleur selon l'une des revendications précédentes, caractérisé en ce que chaque fois deux caisses terminales (4, 4′) des différents échangeurs de chaleur individuels (3, 3a, 3b, 3c, 3d) sont fixées solidement, leurs bords (6) voisins des alésages (5) se faisant face directement.
  7. Agencement d'échangeurs de chaleur selon l'une des revendications précédentes, caractérisé en ce que les caisses terminales (4, 4′) de chaque échangeur individuel (3, 3a, 3b, 3c, 3d) sont usinées dans la zone de contact et sont chacune munies d'un alésage (5), et que dans la zone de contact entre les échangeurs thermiques individuels (3, 3a, 3b, 3c, 3d) on implante un joint.
  8. Agencement d'échangeur thermique selon l'une des revendications précédentes, caractérisé en ce que dans le sens d'écoulement du premier échangeur thermique (1) on place un radiateur d'air turbocompressé (12) d'un moteur thermique turbocompressé et refroidi à l'air, et que la somme des résistances d'air de refroidissement du radiateur d'air turbocompressé (12) et du premier échangeur thermique (1) correspond approximativement à la résistance de l'air de refroidissement du deuxième échangeur thermique.
  9. Agencement d'échangeur thermique selon l'une des revendications précédentes, caractérisé en ce qu'on prévoit un guidage d'air de refroidissement (13) entre les échangeurs thermiques (1, 2) et le ventilateur (9) et que le ventilateur (9) est constitué en soufflante avec une couronne directrice, l'échangeur thermique correspondant étant adapté à la pression d'air de refroidissement plus élevée.
EP19910104510 1990-03-27 1991-03-22 Agencement pour échangeur de chaleur Expired - Lifetime EP0450425B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE59103074T DE59103074D1 (de) 1991-03-22 1991-03-22 Wärmetauscheranordnung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19904009726 DE4009726A1 (de) 1990-03-27 1990-03-27 Waermetauscher-lueftersystem
DE19904033897 DE4033897A1 (de) 1990-10-25 1990-10-25 Waermetauscheranordnung

Publications (3)

Publication Number Publication Date
EP0450425A2 EP0450425A2 (fr) 1991-10-09
EP0450425A3 EP0450425A3 (fr) 1991-10-30
EP0450425B1 true EP0450425B1 (fr) 1994-09-28

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ID=25891567

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19910104510 Expired - Lifetime EP0450425B1 (fr) 1990-03-27 1991-03-22 Agencement pour échangeur de chaleur

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EP (1) EP0450425B1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4142023C2 (de) * 1991-12-19 2001-05-10 Behr Gmbh & Co Wärmetauschereinheit für Kraftfahrzeuge
FR2777643B1 (fr) * 1998-04-20 2000-06-30 Valeo Thermique Moteur Sa Echangeur de chaleur multifonction, en particulier pour vehicule automobile
DE29909871U1 (de) * 1999-06-02 2000-10-12 Autokühler GmbH & Co. KG, 34369 Hofgeismar Wärmeaustauscher, insbesondere Ölkühler
DE10227929A1 (de) * 2002-06-21 2004-01-08 Behr Gmbh & Co. Wärmeübertrageranordnung
DE10328458A1 (de) * 2003-06-25 2005-01-27 Daimlerchrysler Ag Niedrigtemperatur-Kühler für ein Kraftfahrzeug zur Kühlung mehrerer Bauteile
BE1025208B1 (nl) * 2017-05-12 2018-12-12 Cnh Industrial Belgium Nv Koeler met geschrankte kernen voor een voertuig

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2264820A (en) * 1939-05-17 1941-12-02 Fred M Young Combination oil and water cooler
US2505790A (en) * 1946-07-24 1950-05-02 Perfex Corp Combination radiator and oil cooler
DE3344220C2 (de) * 1983-12-07 1987-02-05 Audi AG, 8070 Ingolstadt Wärmetauschvorrichtung, insbesondere für Kraftfahrzeuge

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Publication number Publication date
EP0450425A2 (fr) 1991-10-09
EP0450425A3 (fr) 1991-10-30

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