EP2373934B1 - Évaporateur pour circuit de refroidissement - Google Patents

Évaporateur pour circuit de refroidissement Download PDF

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Publication number
EP2373934B1
EP2373934B1 EP09760524.0A EP09760524A EP2373934B1 EP 2373934 B1 EP2373934 B1 EP 2373934B1 EP 09760524 A EP09760524 A EP 09760524A EP 2373934 B1 EP2373934 B1 EP 2373934B1
Authority
EP
European Patent Office
Prior art keywords
evaporator
heat
region
exchanger element
refrigerant
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
EP09760524.0A
Other languages
German (de)
English (en)
Other versions
EP2373934A1 (fr
Inventor
Gottfried DÜRR
Günther FEUERECKER
Stefan Hirsch
Tobias Isermeyer
Caroline Janzen
Christoph Walter
Achim Wiebelt
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
Mahle 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 Mahle Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP2373934A1 publication Critical patent/EP2373934A1/fr
Application granted granted Critical
Publication of EP2373934B1 publication Critical patent/EP2373934B1/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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/064—Superheater expansion valves
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • 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
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • F25B2600/00—Control issues
    • F25B2600/21—Refrigerant outlet evaporator temperature

Definitions

  • the invention relates to an evaporator for a refrigeration cycle, in particular for a motor vehicle, according to the preamble of claim 1.
  • JP-A-2004 012127 discloses an evaporator according to the preamble of claim 1.
  • the exchanger member allows overheating of the refrigerant leaving the evaporator section by transferring heat defined by the inlet side refrigerant flow to the exiting refrigerant flow. This makes it possible in particular, the refrigerant the evaporator area to flow through with little or no overheating.
  • the refrigerant can also be present in the entire evaporator area as a wet steam phase and thus cause a complete and homogeneous cooling of the evaporator area.
  • the first expansion element means any suitable expansion element such as a fixed throttle, a thermostatic expansion valve (TXV) or an electronically controlled expansion valve. Since the first expansion element is arranged upstream of the exchanger element, the exchanger element can also be regarded as an internal low-pressure heat exchanger of the refrigeration circuit.
  • the evaporator according to the invention thus comprises an evaporator region essentially in heat exchange with the outer space and the exchanger element essentially effecting an internal heat exchange.
  • a second expansion element is provided on the inlet side between the exchanger element and the evaporator region.
  • the inlet-side part of the exchanger element arranged upstream of the evaporator region can transmit an amount of enthalpy to the outlet-side refrigerant flow in a particularly effective manner.
  • the second expansion element is preferably a fixed throttle, which is to be dimensioned accordingly.
  • the second expansion element can also be designed to be adjustable, either as an alternative or in addition to a controllable design of the first expansion element.
  • the first expansion element is designed as the only interface of the evaporator region and the exchanger element to the remaining refrigerant circuit, wherein the first expansion element is designed in particular as a thermostatic expansion valve.
  • the first refrigerant undergoes substantially no overheating in normal operation in the evaporator region, wherein overheating takes place on the outlet side of the evaporator region in the exchanger element.
  • the entire evaporator region is subject to a substantially homogeneous cooling performance, and in particular no load-dependent overheating region is present in the evaporator region in its expansion.
  • the exchanger member is formed in a simple manner as a section of parallel channels, wherein at least one leading channel is in thermal exchange with at least one recirculating channel via a partition wall.
  • Number and length of the channels can be designed depending on the required performance of the exchanger member and given space.
  • the leading channel and the returning channel have a substantially spiral course.
  • a spiral shape in the sense of the invention is to be understood as a circular, elliptical, polygonal or other spiral-shaped arrangement.
  • the evaporator region and the exchanger element are designed as a structurally integrated unit.
  • the evaporator region and the exchanger element can also be embodied as structurally separated units, which, however, in particular are not necessarily mounted at different locations and connected to one another via refrigerant lines.
  • the evaporator region is designed as an air-cooled climatic evaporator for conditioning an air stream, in particular as a flat-tube evaporator.
  • the evaporator is designed as a cooling body for cooling thermally conductive elements connected to the heat sink.
  • evaporator areas particularly high demands are placed on a homogeneous cooling all of the elements regularly.
  • An example of the spatial design of such an evaporator area is in the document EP 1 835 251 A1 described, wherein the heat sink has a flat plate shape with igelartig arranged thereon supports for cylindrical memory cells.
  • the embodiments of the invention embodied as a cooling body evaporator region are not limited to this example.
  • the heat sink may also be formed to cool flat-cells ("coffee-bags") or prismatic cells, be configured as a folded heat sink, or the like.
  • the elements are designed as electrical energy stores, in particular lithium-ion storage cells.
  • Lithium-ion storage cells not only require a high cooling capacity due to their power density, but also place high demands on compliance with a given temperature range in terms of function, operational reliability and service life.
  • a further heat source in particular power electronics, can also be thermally connected to the exchanger element.
  • the exchanger member is only partially designed as an inner heat exchanger of the refrigerant circuit and also allows heat transfer to the outside area, wherein the introduced heat additionally ensures overheating of the refrigerant in the exchanger element.
  • the exchanger element can also be designed without heat exchange with the outside area or as exclusively internal heat exchanger.
  • the heat sink is formed at least in the evaporator region in a sandwich plate construction.
  • a sandwich plate construction Such a construction of a plate evaporator is for example in the document DE 195 28 116 B4 described, wherein a plurality of layers of perforated, in particular solder-plated sheets are stacked one above the other to form the channels for the refrigerant.
  • the exchanger element is also particularly preferably designed in a plate-sandwich construction, in particular in a structural unit with the evaporator region.
  • the in Fig. 1 Evaporator shown comprises an evaporator section 1 and a connected thereto exchanger element 2.
  • the evaporator 1 is designed as a flat-tube evaporator for conditioning of air L for a passenger compartment. To optimize its performance and improve homogeneity, it is divided into six blocks in the present case, through which a refrigerant K flows through in succession.
  • the evaporator region is thus designed as a heat exchanger connected thermally to the outer region, wherein the exchanger element is designed essentially as an inner heat exchanger.
  • a thermostatic expansion valve 3 is arranged as a first expansion member in front of the exchanger member 2, wherein a leading refrigerant flow is controlled by the expansion valve 3.
  • the refrigerant flow exiting the evaporator also flows through the expansion valve, the control taking place as a function of pressure and temperature of the exiting flow. In this way, an overheating of the exiting stream is ensured continuously, which subsequently enters the suction side in a compressor of the refrigeration circuit.
  • a second expansion element 4 in the form of a fixed throttle is provided on the input side of the evaporator region 1 or between exchanger element 2 and evaporator region 1. This ensures that the incoming stream of refrigerant in the region of the exchanger member only partially expands, wherein in this area sufficient for overheating amount of heat is transferred to the exiting stream. In the entire evaporator region 1 can therefore not be superheated refrigerant, so wet steam, with appropriate control.
  • the exchanger member may be designed as parallel, leading back and forth channels 2a, 2b, which are in thermal contact via a wall 2c.
  • Fig. 3 shows various suitable variants of such an arrangement.
  • the embodiments A, C, D and E may be formed as extruded profiles, which include both channels 2a, 2b.
  • Type B consists of two concentric tubes, at the ends of which corresponding feed pieces (not shown) for the refrigerant are arranged.
  • the hydraulic cross section for the recirculating channel is greater than for the leading channel to account for the expansion in the evaporator 1, 2.
  • the exchanger member 2 may be formed as a multi-channel pipe section with the flat tube evaporator 3 as a structurally integrated unit, for example.
  • the expansion valve 3 may be provided on this unit. D the connections of the expansion valve 3 in a known manner, the only interface of the evaporator 1, 2 to the rest of the refrigerant circuit.
  • the second embodiment according to Fig. 4 differs from the first example only in the structural design in particular of the evaporator section 1, but is in the function (see Fig. 2 ) identical.
  • the evaporator region 1 is formed as a plate-shaped heat sink, are mounted on the elements to be cooled (not shown) in the form of lithium-ion storage cells thermally conductive.
  • An example for a specific design of such designed as a heat sink evaporator is in the document EP 1 835 251 A1 described.
  • the heat sink In the constructive detail design of the heat sink is formed in a sandwich-plate construction of stacked, solder-plated sheets or plates, wherein the refrigerant channels are formed by means of pre-punched openings in the sheets. The sheet stack is then soldered flat in a soldering oven.
  • a detailed example of such a construction of an evaporator is from the document DE 195 28 116 B4 known.
  • the exchanger element 2 is provided separated from the plate-shaped heat sink or evaporator region 1 and connected to the latter via refrigerant lines.
  • Fig. 5 is formed in contrast to the second embodiment, the plate-shaped heat sink 1 as an integrated structural unit with the exchanger element 2.
  • Fig. 6 shows an exemplary shape of the refrigerant channels of the exchanger member 2, wherein the parallel, leading and returning channels 2a, 2b are spirally wound with their thermally connecting partition 2c in a plane spiral.
  • a diversion in depth In the middle of the spiral for each of the channels is a diversion in depth, which can be realized for example by a connection hole in the cooling plate.
  • the helical design of the exchanger element 2 counteracts its property as an internal heat exchanger of the refrigeration circuit.
  • a spiral configuration of the exchanger element can also be achieved by winding tubes, for example with cross-sections according to FIG Fig. 3 , be achieved.
  • the return and return channels in the embodiments according to the Fig. 3 and Fig. 6 be reversed, so that the channels 2a are formed as returning and the channels 2b as leading channels.

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

Claims (11)

  1. Evaporateur pour un circuit de refroidissement, en particulier pour un véhicule automobile, comprenant une zone d'évaporateur (1), où un fluide frigorigène traversant la zone d'évaporateur (1) reçoit, dans la zone d'évaporateur (1), de la chaleur provenant d'une zone extérieure,
    où la zone d'évaporateur (1) est disposée, côté entrée, en aval d'un premier organe de détente (3) suivant la direction d'écoulement du fluide frigorigène,
    où un élément échangeur (2) est prévu entre la zone d'évaporateur (1) et le premier organe de détente (3), où de la chaleur peut être transférée, passant du fluide frigorigène en circulation en amont de la zone d'évaporateur (1), au fluide frigorigène en circulation en aval de la zone d'évaporateur (1), caractérisé en ce qu'il est prévu, côté entrée, entre l'élément échangeur (2) et la zone d'évaporateur (1), un deuxième organe de détente (4), et où le premier organe de détente (3) est conçu comme unique interface de la zone d'évaporateur (1) et de l'élément échangeur (2), par rapport à la partie restante du circuit de refroidissement, où le premier organe de détente (3) est conçu en particulier comme un détendeur thermostatique, où l'élément échangeur (2) est configuré comme une partie de conduits parallèles (2a, 2b), où au moins un conduit de flux aller (2a) est en échange thermique avec au moins un conduit de flux retour (2b), via une paroi de séparation (2c).
  2. Evaporateur selon la revendication 1, caractérisé en ce que le premier fluide frigorigène ne subit, au cours d'un fonctionnement normal, pratiquement aucune surchauffe dans la zone d'évaporateur (1), où il se produit une surchauffe dans l'élément échangeur (2), côté sortie de la zone d'évaporateur (1).
  3. Evaporateur selon la revendication 2, caractérisé en ce que le conduit de flux aller (2a) et le conduit de flux retour (2b) présentent un parcours pratiquement en forme de spirale.
  4. Evaporateur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins la zone d'évaporateur (1) et l'élément échangeur (2) sont conçus comme un ensemble structurellement intégré.
  5. Evaporateur selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la zone d'évaporateur (1) et l'élément échangeur (2) sont conçus comme des ensembles structurellement séparés.
  6. Evaporateur selon l'une quelconque des revendications précédentes, caractérisé en ce que la zone d'évaporateur (1) est conçue comme un évaporateur de climatisation traversé par de l'air et servant à la climatisation d'un flux d'air, ladite zone d'évaporateur étant conçue en particulier comme un évaporateur à tubes plats.
  7. Evaporateur selon l'une quelconque des revendications 1 à 5, caractérisé en ce que l'évaporateur (1) est conçu comme un refroidisseur servant au refroidissement d'éléments reliés au refroidisseur de façon thermiquement conductrice.
  8. Evaporateur selon la revendication 7, caractérisé en ce que les éléments sont conçus comme des accumulateurs d'énergie électrique, en particulier comme des cellules accumulatrices à ions lithium.
  9. Evaporateur selon la revendication 7 ou 8, caractérisé en ce qu'une source de chaleur différente des éléments, en particulier une électronique de puissance, est reliée thermiquement à l'élément échangeur (2).
  10. Evaporateur selon l'une quelconque des revendications 7 à 9, caractérisé en ce que le refroidisseur est conçu, au moins dans la zone d'évaporateur (1), en ayant une structure à plaques de type sandwich.
  11. Evaporateur selon la revendication 10, caractérisé en ce que l'élément échangeur est conçu également en ayant une structure à plaques de type sandwich, en particulier en formant un ensemble structurel avec la zone d'évaporateur (1).
EP09760524.0A 2008-12-08 2009-11-25 Évaporateur pour circuit de refroidissement Not-in-force EP2373934B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008060699A DE102008060699A1 (de) 2008-12-08 2008-12-08 Verdampfer für einen Kältekreis
PCT/EP2009/065852 WO2010076101A1 (fr) 2008-12-08 2009-11-25 Évaporateur pour circuit de refroidissement

Publications (2)

Publication Number Publication Date
EP2373934A1 EP2373934A1 (fr) 2011-10-12
EP2373934B1 true EP2373934B1 (fr) 2015-08-19

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Application Number Title Priority Date Filing Date
EP09760524.0A Not-in-force EP2373934B1 (fr) 2008-12-08 2009-11-25 Évaporateur pour circuit de refroidissement

Country Status (5)

Country Link
US (1) US8616012B2 (fr)
EP (1) EP2373934B1 (fr)
CN (1) CN102239374B (fr)
DE (1) DE102008060699A1 (fr)
WO (1) WO2010076101A1 (fr)

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TWI606221B (zh) 2015-07-15 2017-11-21 艾克頌美孚上游研究公司 一倂移除溫室氣體之液化天然氣的生產系統和方法
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FR2913764A1 (fr) * 2007-03-12 2008-09-19 Valeo Systemes Thermiques Echangeur de chaleur et ensemble integre incorporant un tel echangeur

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WO2010076101A1 (fr) 2010-07-08
CN102239374A (zh) 2011-11-09
DE102008060699A1 (de) 2010-06-10
EP2373934A1 (fr) 2011-10-12
US20110296851A1 (en) 2011-12-08
US8616012B2 (en) 2013-12-31
CN102239374B (zh) 2014-04-23

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