EP2107328B1 - Evaporateur - Google Patents

Evaporateur Download PDF

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Publication number
EP2107328B1
EP2107328B1 EP09004110A EP09004110A EP2107328B1 EP 2107328 B1 EP2107328 B1 EP 2107328B1 EP 09004110 A EP09004110 A EP 09004110A EP 09004110 A EP09004110 A EP 09004110A EP 2107328 B1 EP2107328 B1 EP 2107328B1
Authority
EP
European Patent Office
Prior art keywords
evaporator
flow
fluid
refrigerant
fluid passages
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.)
Not-in-force
Application number
EP09004110A
Other languages
German (de)
English (en)
Other versions
EP2107328A1 (fr
Inventor
Dirk Neumeister
Achim Wiebelt
Jürgen Grünwald
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
Priority claimed from DE102008017113A external-priority patent/DE102008017113A1/de
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP2107328A1 publication Critical patent/EP2107328A1/fr
Application granted granted Critical
Publication of EP2107328B1 publication Critical patent/EP2107328B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F28D2021/0085—Evaporators

Definitions

  • the invention relates to an evaporator, in particular for a motor vehicle, and a device for cooling a heat source of a motor vehicle
  • DE 10 2004 036 951 A1 proposes to use a built-up of parallel, interconnected plates heat exchanger, the type of which is also referred to as a stacked-plate heat exchanger to use as an evaporator of a refrigeration cycle of a motor vehicle.
  • a plate type heat exchanger used as an evaporator in order to ensure sufficient evaporation and, in particular, to ensure sufficient overheating of the vaporized refrigerant, it is required that the plate length in the flow direction of the refrigerant be sufficiently large, thereby being generally larger than a plate width across to the flow direction of the refrigerant. This results in restrictions on the dimensions of the evaporator depending on the given space.
  • the US 2002/0179 295 A1 discloses a cullet evaporator for an automotive air conditioning system, wherein a dimension "l" is between 20 mm and 55 mm.
  • FIG. 8 shows in FIG. 8 an evaporator, in particular for a motor vehicle, comprising a plurality of plates stacked parallel to one another in a vertical direction with aligned apertures for supplying and discharging a first fluid designed as a refrigerant and a second fluid, wherein between two adjacent plates, a flow channel of the first type for guiding the first fluid in alternation with a flow channel of the second type for guiding the second fluid are formed, wherein a heat transfer surface of the plates has a length in the flow direction of the refrigerant and a perpendicular thereto Width, wherein the refrigerant the flow channels in a first, one or more of the flow channels of the first kind comprehensive flood and at least one of the first flood following a deflection subsequent, one or more of the flow channels of the first kind flowing through the second flood.
  • the refrigerant flows through at least a first and second tide of the evaporator .
  • a tide in the context of the invention is to be understood by the evaporator over its length sweeping flow path of the refrigerant, wherein successive floods generally parallel to each other and in the opposite direction, so that the refrigerant undergoes a deflection between the two successive floods. Due to the deflection and the passage of successive floods, the flow path of the refrigerant in the evaporator is extended even in a short design, so that sufficient overheating can be ensured.
  • the ratio of the length to the width UB is not less than about 0.5, in particular not less than about 0.7.
  • the heat exchanger is designed with respect to the refrigerant in such a design with exactly two floods useful as a U-flow heat exchanger.
  • the refrigerant flows through at least a third, one or more flow channels of the first kind comprehensive tide, which follows a secondary flow downstream of the second deflection.
  • the second tide has at least as many flow channels as the first tide and up to 50% more flow channels than the first tide.
  • the third tide has at least as many flow channels as the second tide and up to 200% more flow channels than the second tide.
  • “approximately equal” means that a number of flow channels of one tide deviate slightly from the number of the other two tides.
  • the number of flow channels of the first and third floods can be six and the number of second floods seven.
  • the second fluid flows through the evaporator in at least two floods, each comprising one or more of the flow channels of the second type.
  • the evaporator would be expediently designed as a U-flow heat exchanger with respect to the second fluid.
  • it can also be designed in a simple manner as an I-flow heat exchanger with only one tide for the second fluid.
  • more than two floods may be provided for the second fluid.
  • the second fluid is a liquid coolant.
  • a separation of successive floods is formed by a special plate different from other plates, which has an obstruction instead of one or more of the openings.
  • a multi-flow evaporator is designed according to the design of a plate heat exchanger in a simple manner.
  • the special plate has both an obstruction for the separation of floods of Refrigerant as well as an obstruction to separate flooding of the second fluid. In this way, the number of special plates is kept very small and the number of other, generally formed as equal parts plates of the heat exchanger is kept particularly large.
  • the flow direction of the last of the floods is generally preferred for the flow direction of the last of the floods to be essentially in the direction of the force of gravity. This can prevent the refrigerant from accumulating in the evaporator.
  • substantially in the direction of gravity is thus also to be understood any deviation from the exact direction of gravity, which still allows a sufficiently large influence of gravity on the outflow of the refrigerant.
  • An inventive evaporator is particularly well suited to be provided in a refrigerant circuit or the air conditioning system of a motor vehicle in order to cool a heat source of the motor vehicle via a coolant circuit. Due to the compact design of the evaporator, the increasingly critical space conditions in modern motor vehicles can be taken into account.
  • the heat source is a traction battery of the motor vehicle, in particular a lithium-ion battery.
  • a traction battery of the motor vehicle in particular a lithium-ion battery.
  • Such batteries which are used not only in pure electric vehicles but especially in hybrid vehicles with an electric motor and an internal combustion engine, high demands are placed on the cooling to ensure durability and reliability.
  • an inventive, small-sized evaporator of high heat exchanger performance which is arranged between a coolant circuit and a particular air conditioning of the vehicle serving refrigeration circuit (also called "chiller") is particularly suitable.
  • the compressor of the refrigeration circuit may expediently be arranged directly downstream of the second evaporator. This is to be understood in particular that no collector between evaporator and compressor is arranged and space reasons, no integrated into the evaporator collector is provided.
  • the schematic sectional view Fig. 1 shows a vaporizer according to the prior art.
  • a plurality of plates 1 are stacked in parallel in a vertical direction h, wherein a flow channel of the first type 2 and a flow channel of the second type 3 alternately remain between two plates.
  • the plates 1 have mutually aligned apertures 1 a, 1 b, are formed by the tubular, extending in the vertical direction feeds and discharges for a refrigerant or first fluid and a second fluid of the evaporator.
  • the openings 1a, 1 b in a known manner alternately raised edges (not shown), which are soldered sealingly with the adjacent plate.
  • the plates are made of an aluminum alloy.
  • the stack of plates 1 is closed in a known manner at its two ends by end plates 9, to which the supply lines and outlets for the refrigerant and the second fluid are attached.
  • Fig. 2 shows a first embodiment of an evaporator according to the invention, in which the evaporator with respect to the refrigerant in three floods 4, 5, 6 is divided.
  • the separation of the flow channels 1 in the individual floods 4, 5, 6 takes place by special plates 7, in which at least one of the openings 1a, 1b is replaced by an obstruction 7a.
  • the obstructions 7a prevent the refrigerant from a complete flow through the supply or discharge in the vertical direction.
  • a width direction of the evaporator is perpendicular to the plane of the drawing Fig. 2 and thus perpendicular to the longitudinal direction and to the vertical direction h.
  • the plates 1 have between the feeders and drains 1a, 1b a heat transferring surface having a length L in the longitudinal direction and a width B in the width direction.
  • L is about 4 cm and B about 5.5 cm. This results in a ratio of UB of about 0.73.
  • a height H of the stack of plates 1 is about 4 cm.
  • the external dimensions of the evaporator for this particular example have a total length of 8.8 cm, a total width of 6.2 cm and a height of 4 cm.
  • the plates 1 Between the individual plates 1 no turbulence inserts are provided at least on the side of the refrigerant. Depending on requirements, the plates 1 have indentations and structuring in order to increase the surface area and introduce turbulence into the flowing refrigerant.
  • the flow channels of the second type 3 are shown by broken lines and are in the present case flows through by a liquid coolant of a coolant circuit as a second fluid
  • the feeds and discharges for the second fluid are not shown.
  • Fig. 3 shows a further embodiment of an evaporator according to the invention.
  • the refrigerant only flows through two floods 4, 5, so that the throughflow path of the refrigerant as a whole is U-shaped (U-flow heat exchanger).
  • the dimensions of the plates 1 are the same as in the first embodiment.
  • the path of the coolant through the flow channels of the second type 3 is divided into a plurality of floods.
  • Fig. 3 a representation of the floods of the second fluid or coolant, wherein the illustration Fig. 2 shows the floods of the refrigerant of the same evaporator.
  • both fluids are divided into several floods, it may be expedient for one or more of the special plates 7 to have both an obstruction for the first fluid and an obstruction for the second fluid. This makes it possible to reduce the number of special plates required and increase the total number of identical parts of the evaporator.
  • Fig. 4 shows a device for cooling a heat source 10 of a motor vehicle, in this case a lithium-ion battery of a hybrid drive.
  • the battery 10 is cooled by a circuit with liquid coolant, which is circulated via a circulation pump 11.
  • the heat absorbed by the battery 10 is dissipated via a heat exchanger 12, the an inventive evaporator according to one of the preceding embodiments is.
  • the evaporator 12 is integrated in a refrigeration circuit 13, which also serves for air conditioning of the motor vehicle.
  • the refrigerant is compressed by a compressor 14 and subsequently cooled by a condenser or gas cooler 15
  • the condenser or gas cooler 15 below are an air conditioner 16 and the evaporator 12 according to the invention connected in parallel, wherein before each of the evaporator 12, 16 each have an expansion element 16a, 12a is arranged.
  • a fan 17 delivers air for conditioning by the A / C evaporator 16.
  • Fig. 5 shows a modification of the device Fig. 4 in which the coolant circuit in addition to the evaporator 16 still has a parallel-connected auxiliary cooler 18, which is flowed around by outside air.
  • the coolant can selectively flow through the evaporator 12, the Bruchler 18 or both heat exchangers 12, 18 to ensure optimal cooling of battery 10 and the vehicle interior in all operating situations.

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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)
  • Air-Conditioning For Vehicles (AREA)

Claims (14)

  1. Evaporateur, en particulier pour un véhicule automobile, comprenant
    une pluralité de plaques (1) parallèles entre elles et empilées dans le sens de la hauteur, comportant des ouvertures (1a, 1b) disposées de façon alignée et servant à l'alimentation et à l'évacuation d'un premier fluide conçu comme un fluide frigorigène et d'un deuxième fluide conçu comme un moyen de refroidissement liquide,
    où sont configurés, entre deux plaques adjacente (1), un conduit d'écoulement (2), d'un premier type, servant au guidage du premier fluide, et, en alternance, un conduit d'écoulement (3), d'un deuxième type, servant au guidage du deuxième fluide,
    où une surface des plaques (1), transmettant de la chaleur, présente une longueur (L) dans le sens de l'écoulement du fluide frigorigène et une largeur (B) perpendiculaire à cette longueur,
    où l'évaporateur peut être intégré aussi bien dans un circuit de fluide frigorigène que dans un circuit d'un moyen de refroidissement, où le rapport (L/B) de la longueur, sur la largeur, n'est pas supérieur à 1,3 environ,
    où le fluide frigorigène traverse les conduits d'écoulement (2) dans un premier flux (4) comprenant un ou plusieurs des conduits d'écoulement (2) du premier type, et au moins dans un deuxième flux (5) faisant suite au premier flux après un retour de flux (8) et comprenant un ou plusieurs des conduits d'écoulement (2) du premier type.
  2. Evaporateur selon la revendication 1, caractérisé en ce que le rapport L/B de la longueur, sur la largeur, n'est pas inférieur à 0,5 environ, en particulier non inférieur à 0,7 environ.
  3. Evaporateur selon l'une ou l'autre des revendications précédentes, caractérisé en ce que s'applique la relation 1 <= n2/n1 <= 3 pour le rapport du nombre de conduits d'écoulement du deuxième flux (n2), relativement au nombre de conduits d'écoulement du premier flux (n1).
  4. Evaporateur selon la revendication 3, caractérisé en ce qu'il est prévu exactement deux flux (4, 5) pour le fluide frigorigène.
  5. Evaporateur selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le fluide frigorigène traverse un troisième flux (6) comprenant un ou plusieurs conduits d'écoulement (2) du premier type, flux qui succède à un deuxième retour de flux (8) faisant suite au deuxième flux (5).
  6. Evaporateur selon la revendication 5, caractérisé en ce que s'applique la relation 1 <= n2/n1 <= 1,5 pour le rapport du nombre de conduits d'écoulement du deuxième flux (n2), relativement au nombre de conduits d'écoulement du premier flux (n1).
  7. Evaporateur selon la revendication 5 ou 6, caractérisé en ce que s'applique la relation 1 <= n3/n2 <= 3 pour le rapport du nombre de conduits d'écoulement du troisième flux (n3), relativement au nombre de conduits d'écoulement du deuxième flux (n2).
  8. Evaporateur selon l'une quelconque des revendications 5 à 7, caractérisé en ce que le nombre de conduits d'écoulement du troisième flux (n3), le nombre de conduits d'écoulement du deuxième flux (n2) et le nombre de conduits d'écoulement du premier flux (n1) sont presque égaux ou identiques.
  9. Evaporateur selon l'une quelconque des revendications précédentes, caractérisé en ce que le deuxième fluide traverse l'évaporateur dans au moins deux flux qui comprennent à chaque fois un ou plusieurs conduits d'écoulement (3) du deuxième type.
  10. Evaporateur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une séparation de flux (4, 5, 6) se succédant est formée par une plaque spéciale (7) différente des autres plaques (1), plaque spéciale qui, à la place d'une ou de plusieurs ouvertures, présente une obturation (7a).
  11. Evaporateur selon la revendication 10, caractérisé en ce que la plaque spéciale (7) présente aussi bien une obturation (7a) pour la séparation de flux du fluide frigorigène, qu'une obturation pour la séparation de flux du deuxième fluide.
  12. Dispositif servant au refroidissement d'une source de chaleur d'un véhicule automobile, comprenant un circuit de fluide frigorigène comportant un compresseur (14), un condenseur ou un refroidisseur de gaz (15), un premier évaporateur (16) servant au conditionnement d'air de l'habitacle d'un véhicule et un deuxième évaporateur (12),
    où le deuxième évaporateur (12) est en échange thermique avec un circuit d'un moyeu de refroidissement refroidissant la source de chaleur (10),
    où le deuxième évaporateur (12) est conçu comme un évaporateur selon l'une quelconque des revendications 1 à 11.
  13. Dispositif selon la revendication 12, caractérisé en ce que la source de chaleur (10) est une batterie de traction du véhicule automobile, en particulier une batterie lithium-ion.
  14. Dispositif selon la revendication 12 ou 13, caractérisé en ce que le compresseur (14) est disposée dans le circuit de fluide frigorigène, en faisant suite directement au deuxième évaporateur (12).
EP09004110A 2008-04-02 2009-03-23 Evaporateur Not-in-force EP2107328B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008017113A DE102008017113A1 (de) 2008-04-02 2008-04-02 Verdampfer
DE102008044673 2008-08-28

Publications (2)

Publication Number Publication Date
EP2107328A1 EP2107328A1 (fr) 2009-10-07
EP2107328B1 true EP2107328B1 (fr) 2012-07-11

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP09004110A Not-in-force EP2107328B1 (fr) 2008-04-02 2009-03-23 Evaporateur

Country Status (2)

Country Link
US (1) US20090249810A1 (fr)
EP (1) EP2107328B1 (fr)

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DE102011081886A1 (de) 2011-08-31 2013-02-28 Behr Gmbh & Co. Kg Wärmeübertrager
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DE102015205933A1 (de) * 2015-04-01 2016-10-06 Mahle International Gmbh Wärmeübertrager oder Chiller
WO2017201252A1 (fr) * 2016-05-20 2017-11-23 Modine Manufacturing Company Échangeur de chaleur et système d'échange de chaleur
CN110186300B (zh) * 2019-06-27 2024-10-15 浙江银轮机械股份有限公司 板片、板片组件及热交换器

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US20090249810A1 (en) 2009-10-08
EP2107328A1 (fr) 2009-10-07

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