EP1153256A1 - A condenser - Google Patents

A condenser

Info

Publication number
EP1153256A1
EP1153256A1 EP00901764A EP00901764A EP1153256A1 EP 1153256 A1 EP1153256 A1 EP 1153256A1 EP 00901764 A EP00901764 A EP 00901764A EP 00901764 A EP00901764 A EP 00901764A EP 1153256 A1 EP1153256 A1 EP 1153256A1
Authority
EP
European Patent Office
Prior art keywords
condenser
refrigerant
tubes
flowpaths
condenser according
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.)
Withdrawn
Application number
EP00901764A
Other languages
German (de)
French (fr)
Inventor
Adrian Jackson
Roy Redhead
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.)
Marelli Automotive Systems UK Ltd
Original Assignee
Llanelli Radiators Ltd
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 Llanelli Radiators Ltd filed Critical Llanelli Radiators Ltd
Publication of EP1153256A1 publication Critical patent/EP1153256A1/en
Withdrawn legal-status Critical Current

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
    • 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
    • F28F9/0212—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions the partitions being separate elements attached to header boxes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3227—Cooling devices using compression characterised by the arrangement or the type of heat exchanger, e.g. condenser, 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F28D1/053—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 the conduits being straight
    • F28D1/0535—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 the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
    • F28F1/045—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular with assemblies of stacked 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
    • 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
    • F28D2021/0084—Condensers

Definitions

  • the present invention relates to a condenser, and in particular to a condenser for use in an air conditioning or refrigeration system (particularly for automotive use) .
  • EP-B- 0219974 discloses a condenser for an automotive refrigeration/air conditioning system in which condenser refrigerant flow tubes have a hydraulic diameter in the range 0.381mm to 1.778mm. Hydraulic diameters at approximately 0.9mm are said to optimise ultimate heat transfer efficiency.
  • a condenser for use in an air conditioning or refrigeration system, the condenser comprising a plurality of refrigerant flowpaths extending adjacent one another, said flowpaths being grouped such that adjacent groups carry refrigerant passes in opposed directions across the condenser, wherein the arrangement of groups is such that the number of refrigerant passes across the condenser is 5 or above.
  • the hydraulic diameter of refrigerant flowpaths in a respective pass is preferably substantially at or above l.' ⁇ mm. Most preferably, the hydraulic diameter of passes is substantially at or above 1.75mm.
  • a further benefit and significant advantage is that, particularly at flowpath hydraulic diameters in the preferred range, reduced refrigerant pressure drop is found to occur across the condenser. This is of significant technical benefit in that the overall system energy requirements are reduced.
  • the number of refrigerant passes across the condenser is 10 or less.
  • the refrigerant flowpaths are preferably substantially parallel to one another across the condenser.
  • the condenser is desirably air cooled.
  • the refrigerant flowpaths typically comprise tubes (preferably flattened tubes) extending across the condenser, the tubes preferably including internal flowpath dividers arranged to divide the tube into a plurality of flowpaths.
  • the internal flowpath dividers may comprise inserts for respective tubes.
  • An airflow matrix is preferably provided intermediate adjacent tubes.
  • the airflow matrix preferably comprises a series of fins or louvres.
  • the number of tubes in at least one pass grouping is preferably substantially in the range 2 to 12.
  • the number of tubes in the most upstream grouping is preferably substantially in the range 12 or less.
  • the condenser comprises spaced headers between which the refrigerant flowpaths extend.
  • the headers preferably include internal dividers directing the flow of refrigerant along adjacent passes through respective groups of refrigerant flow paths .
  • Flowpaths in an upstream pass grouping preferably have a greater effective cross sectional area than flowpaths in a downstream pass group.
  • Figure 1 is a schematic representation of an exemplary condenser according to the invention
  • Figure 2 is an end view of a condenser tube used in the condenser of figure 1;
  • Figure 3 is a graphical representation of condenser performance characteristics for prior art condensers and condensers according to the invention.
  • Figure 4 is a further graphical representation of condenser performance characteristics for prior art condensers and condensers according to the invention.
  • a condenser for use in an automotive air conditioning system.
  • the condenser 1 comprises a pair of spaced headers 2, 3 ; header 2 is provided with an upstream inlet 4 for refrigerant vapour, whereas header 3 is provided with a downstream condensate outlet 5.
  • header 2 is provided with an upstream inlet 4 for refrigerant vapour
  • header 3 is provided with a downstream condensate outlet 5.
  • the refrigerant enters via inlet 4 in vapour phase and passes, in succession, through banks 7a, 7b, 7c, 7d and 7e of condenser tubes 6 before the refrigerant condensate exits via outlet 5.
  • each bank comprising a series of tubes 6 extending between the headers and spaced by inter-tube airways permitting cooling air to be drawn (typically by a fan) through the condenser in an airflow direction transverse to the longitudinal direction of tubes 6.
  • the airways may be defined by inter-tube fins defining an airway matrix of maximum heat transfer area as is conventional in the condenser art and described in, for example, EP-B-0219974.
  • each tube 6 includes a number of internal divisions defining smaller flow channels 8, such that the hydraulic diameter of the channels 8 (and for each tube 6) is approximately 1.730mm.
  • the hydraulic diameter needs to be at least 1.5mm (preferably at least 1.65mm).
  • the headers 2, 3 are provided with internal baffles 9 ensuring that the refrigerant follows a serpentine path through the condenser to flow along a path through adjacent banks (7a, 7b; 7b, 7c; 7c, 7d; 7d, 7e) in opposed pass directions across the condenser 1.
  • curve A represents the performance of a known type 4 -pass condenser having a Hydraulic Diameter (Dh) of 1.023 mm (falling within the range specified in EP-B-0219974) .
  • Curve C represents characteristics of a condenser according to the invention having a five refrigerant pass regime, as described above and shown in Figure 1, in which the number of tubes 6 per pass (i.e.
  • Curve B represents a condenser according to the invention having six passes (i.e. banks 7) having from inlet to outlet banks 7 including 10-7-6-5- 4-3 tubes per bank/pass respectively.
  • the Hydraulic Diameter (Dh) of the tubes in the condensers represented by curves B and C are 1.730mm.
  • Figure 4 shows corresponding curves for A, B and C detailing refrigerant pressure drop and refrigerant flow rate.
  • the increased number of passes for condensers according to the invention provides thermal performance characteristics approaching closely the performance of condensers falling in the range of EP-B-0219974.
  • the air side pressure drop is not significantly affected when compared to the known condenser.
  • the five and six pass condensers 1 of the invention exhibit significantly less refrigerant pressure drop across the condenser than the known condenser (curve A) . This means that the refrigeration system compressor is required to carry out less work and results in overall energy savings for systems employing condensers according to the invention.
  • a further benefit of the invention is that it enables adequate condenser performance to be achieved outside the Hydraulic Diameter range specified in EP-B-0219974.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

A condenser (1) for use in an air conditioning or refrigeration system has refrigerant flowpaths (8) extending adjacent one another and grouped such that adjacent groups (7a, 7b; 7b, 7c; 7c, 7d; 7d, 7e) carry refrigerant passes in opposed directions across the condenser. The arrangement of groups (7) is such that the number of refrigerant passes across the condenser is 5 or above and the hydraulic diameter of paths in respective pass is 1.5mm or above.

Description

A Condenser
The present invention relates to a condenser, and in particular to a condenser for use in an air conditioning or refrigeration system (particularly for automotive use) .
EP-B- 0219974 discloses a condenser for an automotive refrigeration/air conditioning system in which condenser refrigerant flow tubes have a hydraulic diameter in the range 0.381mm to 1.778mm. Hydraulic diameters at approximately 0.9mm are said to optimise ultimate heat transfer efficiency.
An improved condenser has now been devised.
According to the invention, there is provided a condenser for use in an air conditioning or refrigeration system, the condenser comprising a plurality of refrigerant flowpaths extending adjacent one another, said flowpaths being grouped such that adjacent groups carry refrigerant passes in opposed directions across the condenser, wherein the arrangement of groups is such that the number of refrigerant passes across the condenser is 5 or above.
It has been found that, particularly for flowpaths having hydraulic diameters toward the upper end of the preferred range specified in EP-B-0219947 and above, by increasing the number of passes compared to conventional condenser designs (which typically have four or less passes) at least comparable thermal performance is achieved. The hydraulic diameter of refrigerant flowpaths in a respective pass is preferably substantially at or above l.'βmm. Most preferably, the hydraulic diameter of passes is substantially at or above 1.75mm.
A further benefit and significant advantage is that, particularly at flowpath hydraulic diameters in the preferred range, reduced refrigerant pressure drop is found to occur across the condenser. This is of significant technical benefit in that the overall system energy requirements are reduced.
Desirably, the number of refrigerant passes across the condenser is 10 or less.
The refrigerant flowpaths are preferably substantially parallel to one another across the condenser. The condenser is desirably air cooled.
The refrigerant flowpaths typically comprise tubes (preferably flattened tubes) extending across the condenser, the tubes preferably including internal flowpath dividers arranged to divide the tube into a plurality of flowpaths. The internal flowpath dividers may comprise inserts for respective tubes. An airflow matrix is preferably provided intermediate adjacent tubes. The airflow matrix preferably comprises a series of fins or louvres.
The number of tubes in at least one pass grouping is preferably substantially in the range 2 to 12. The number of tubes in the most upstream grouping is preferably substantially in the range 12 or less.
The condenser comprises spaced headers between which the refrigerant flowpaths extend. The headers preferably include internal dividers directing the flow of refrigerant along adjacent passes through respective groups of refrigerant flow paths .
Flowpaths in an upstream pass grouping preferably have a greater effective cross sectional area than flowpaths in a downstream pass group.
The invention will now be further described in a specific embodiment by way of example only, and with reference to the accompanying drawings, in which:
Figure 1, is a schematic representation of an exemplary condenser according to the invention; Figure 2, is an end view of a condenser tube used in the condenser of figure 1;
Figure 3 is a graphical representation of condenser performance characteristics for prior art condensers and condensers according to the invention; and,
Figure 4, is a further graphical representation of condenser performance characteristics for prior art condensers and condensers according to the invention.
Referring to the drawings and, initially to Figures 1 and
2, there is shown a condenser (generally designated 1) for use in an automotive air conditioning system. The condenser 1 comprises a pair of spaced headers 2, 3 ; header 2 is provided with an upstream inlet 4 for refrigerant vapour, whereas header 3 is provided with a downstream condensate outlet 5. (For a six pass condenser, both inlet and outlet would be in the same header.) In passing through the condenser 1, the refrigerant enters via inlet 4 in vapour phase and passes, in succession, through banks 7a, 7b, 7c, 7d and 7e of condenser tubes 6 before the refrigerant condensate exits via outlet 5.
In the embodiment described, there are five banks of tubes 7, each bank comprising a series of tubes 6 extending between the headers and spaced by inter-tube airways permitting cooling air to be drawn (typically by a fan) through the condenser in an airflow direction transverse to the longitudinal direction of tubes 6. The airways may be defined by inter-tube fins defining an airway matrix of maximum heat transfer area as is conventional in the condenser art and described in, for example, EP-B-0219974.
For performance of the invention it is required that at least five banks 7 of tubes 6 are provided, requiring the refrigerant to undergo a minimum of five passes across the heat exchanger before exiting via outlet 5. This is greater than the conventional number of passes employed in known condensers. Furthermore, the number of tubes per pass (particularly the refrigerant pass via initial bank 7a) is reduced compared to known heat exchanger types. In the five pass embodiment shown in Figure 1, the arrangement has tubes 6 in each bank as follows:
Bank Number of Tubes
7a 12
7b 9
7c 7
7d 4
7e 3 (Other embodiments of five pass condensers may have other tube number arrangements. In a six pass condenser according to the invention utilising six banks 7 of tubes 6, an arrangement suggested might be 10-7-6-5-4-3 but could be other combinations.)
In condensers according to the invention for which tests have been carried out, each tube 6 includes a number of internal divisions defining smaller flow channels 8, such that the hydraulic diameter of the channels 8 (and for each tube 6) is approximately 1.730mm. Experimental evidence suggests that for performance of the invention, the hydraulic diameter needs to be at least 1.5mm (preferably at least 1.65mm).
The headers 2, 3 are provided with internal baffles 9 ensuring that the refrigerant follows a serpentine path through the condenser to flow along a path through adjacent banks (7a, 7b; 7b, 7c; 7c, 7d; 7d, 7e) in opposed pass directions across the condenser 1.
It has been found that by providing the condenser having five and more passes across the condenser (particularly where hydraulic diameters are in the range mentioned above) , desirable condenser performance characteristics are achieved when compared with other forms of known condensers . Referring to Figure 3, in the graph, curve A represents the performance of a known type 4 -pass condenser having a Hydraulic Diameter (Dh) of 1.023 mm (falling within the range specified in EP-B-0219974) . Curve C represents characteristics of a condenser according to the invention having a five refrigerant pass regime, as described above and shown in Figure 1, in which the number of tubes 6 per pass (i.e. per bank 7) are arranged as follows from inlet to outlet (12-9-7-4-3) . Curve B represents a condenser according to the invention having six passes (i.e. banks 7) having from inlet to outlet banks 7 including 10-7-6-5- 4-3 tubes per bank/pass respectively. The Hydraulic Diameter (Dh) of the tubes in the condensers represented by curves B and C are 1.730mm.
Figure 4 shows corresponding curves for A, B and C detailing refrigerant pressure drop and refrigerant flow rate.
As shown in Figures 3 and 4, the increased number of passes for condensers according to the invention (curves B and C) provides thermal performance characteristics approaching closely the performance of condensers falling in the range of EP-B-0219974. As also shown in Figure 3, the air side pressure drop is not significantly affected when compared to the known condenser. Furthermore, as shown in Figure 4, the five and six pass condensers 1 of the invention (curves B and C) exhibit significantly less refrigerant pressure drop across the condenser than the known condenser (curve A) . This means that the refrigeration system compressor is required to carry out less work and results in overall energy savings for systems employing condensers according to the invention.
The beneficial reduction in pressure drop for a given performance level is unexpected and offers potential benefit in refrigeration and air conditioning systems, particularly where refrigerant pressures and pressure losses are significant. Such a situation could, for example, be in sub-cooling systems where condensing pressures are increased as a direct consequence of reduced condensing volumes .
A further benefit of the invention is that it enables adequate condenser performance to be achieved outside the Hydraulic Diameter range specified in EP-B-0219974.

Claims

Claims :
1. A condenser for use in an air conditioning or refrigeration system, the condenser comprising a plurality of refrigerant flowpaths extending adjacent one another, flowpaths being grouped such that adjacent groups carry refrigerant passes in opposed directions across the condenser, wherein the arrangement of groups is such that the number of refrigerant passes across the condenser is 5 or above.
2. A condenser according to claim 1, wherein the arrangement of groups is such that the number of refrigerant passes across the condenser is 6 or above.
3. A condenser according to claim 1, wherein the arrangement of groups is such that the number of refrigerant passes across the condenser is 7 or above.
4. A condenser according to claim 1, wherein the arrangement of groups is such that the number of refrigerant passes across the condenser is 8 or above.
5. A condenser according to any of claims 1 to 4, wherein the number of refrigerant passes across the condenser is 10 or less.
6. A condenser arrangement according to any preceding claim, wherein refrigerant flowpaths comprise tubes extending across the condenser.
7. A condenser according to claim 6, wherein the number of tubes in at least one pass is substantially in the range 2 to 12.
8. A condenser according to claim 7, wherein the number of tubes in the most upstream group is substantially in the range 12 or less.
9. A condenser according to any preceding claim wherein the hydraulic diameter of paths in a respective pass is substantially at or above 1.5mm.
10. A condenser according to any preceding claim, wherein the hydraulic diameter of passes is substantially at or above 1.8mm.
11. A condenser according to any preceding claim, wherein flowpaths in an upstream pass grouping preferably have a greater effective cross sectional area than flowpaths in a downstream pass group.
12. A condenser according to any preceding claim, wherein the condenser comprises spaced headers between which -lithe refrigerant extends.
13. A condenser according to claim 12, wherein the headers include internal dividers directing the flow of refrigerant along adjacent passes through respective groups of refrigerant flow paths .
14. A condenser according to any preceding claim wherein the refrigerant flow paths comprise tubes extending across the condenser, the tubes including internal flowpath dividers arranged to divide the tube into a plurality of flow channels.
15. A condenser according to claim 14, wherein the internal flowpath dividers comprise inserts for respective tubes.
16. A condenser according to any preceding claim, wherein the refrigerant flowpaths comprise flattened tubes extending across the condenser.
17. A condenser according to any preceding claim, wherein the refrigerant flowpaths comprise tubes extending across the condenser an airflow matrix being provided intermediate adjacent tubes.
18. A condenser according to claim 17, wherein the airflow matrix comprises a series of fins.
19. A condenser substantially as herein described with reference to the accompanying drawings.
EP00901764A 1999-02-11 2000-02-03 A condenser Withdrawn EP1153256A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB9903050 1999-02-11
GB9903050A GB2346680A (en) 1999-02-11 1999-02-11 Condenser
PCT/GB2000/000307 WO2000047939A1 (en) 1999-02-11 2000-02-03 A condenser

Publications (1)

Publication Number Publication Date
EP1153256A1 true EP1153256A1 (en) 2001-11-14

Family

ID=10847516

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00901764A Withdrawn EP1153256A1 (en) 1999-02-11 2000-02-03 A condenser

Country Status (4)

Country Link
EP (1) EP1153256A1 (en)
AU (1) AU2306400A (en)
GB (1) GB2346680A (en)
WO (1) WO2000047939A1 (en)

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US20020195240A1 (en) * 2001-06-14 2002-12-26 Kraay Michael L. Condenser for air cooled chillers
US20030140647A1 (en) * 2002-01-31 2003-07-31 Gawthrop Peter Rex Receiverless air conditioning system
GB0326443D0 (en) * 2003-11-13 2003-12-17 Calsonic Kansei Uk Ltd Condenser
EP2107328B1 (en) * 2008-04-02 2012-07-11 Behr GmbH & Co. KG Vaporiser
DE102011007784A1 (en) * 2011-04-20 2012-10-25 Behr Gmbh & Co. Kg capacitor
JP5858478B2 (en) * 2012-09-04 2016-02-10 シャープ株式会社 Parallel flow type heat exchanger and air conditioner equipped with the same
DE102013204294A1 (en) * 2013-03-12 2014-10-02 Behr Gmbh & Co. Kg Condenser assembly for refrigerant
JP7164286B2 (en) * 2016-04-27 2022-11-01 東芝ライフスタイル株式会社 refrigerator
FR3112312B1 (en) * 2020-07-08 2022-09-02 Valeo Systemes Thermiques Thermal management device for the batteries of an electric or hybrid motor vehicle

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Title
See references of WO0047939A1 *

Also Published As

Publication number Publication date
WO2000047939A1 (en) 2000-08-17
GB2346680A (en) 2000-08-16
GB9903050D0 (en) 1999-03-31
AU2306400A (en) 2000-08-29

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