EP1319907A2 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP1319907A2
EP1319907A2 EP02258119A EP02258119A EP1319907A2 EP 1319907 A2 EP1319907 A2 EP 1319907A2 EP 02258119 A EP02258119 A EP 02258119A EP 02258119 A EP02258119 A EP 02258119A EP 1319907 A2 EP1319907 A2 EP 1319907A2
Authority
EP
European Patent Office
Prior art keywords
header pipe
heat exchanger
refrigerant
tubes
tube
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Withdrawn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
EP02258119A
Other languages
German (de)
English (en)
Other versions
EP1319907A3 (fr
Inventor
Kenichi c/o Sanden Corporation Wada
Hirotaka C/O Sanden Corporation Kado
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.)
Sanden Corp
Original Assignee
Sanden Corp
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 Sanden Corp filed Critical Sanden Corp
Publication of EP1319907A2 publication Critical patent/EP1319907A2/fr
Publication of EP1319907A3 publication Critical patent/EP1319907A3/fr
Withdrawn legal-status Critical Current

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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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0441—Condensers with an integrated receiver containing a drier or a filter
    • 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
    • F25B2400/02—Centrifugal separation of gas, liquid or oil

Definitions

  • the present invention relates to a heat exchanger including a desiccant unit inserted into one of header pipes for use in an air conditioner for vehicles.
  • the present invention relates to a heat exchanger suitable use as a condenser in an air conditioner for vehicles.
  • Heat exchangers for use in an air conditioner for vehicles which include a pair of header pipes and a plurality of heat exchanger tubes communicated therebetween, are known in the art. As shown in Figs. 4 and 5, a heat exchanger 100 has a pair of header pipes 101 and 102. The pair of header pipes 101 and 102 is communicated by a plurality of heat exchanger tubes 103. A diameter of header pipe 102 is larger than that of header pipe 101. A desiccant unit 104 is inserted into herder pipe 102.
  • heat exchanger 100 As shown in Fig. 4, in such heat exchanger 100, because header pipe 102 having desiccant unit 104 protrudes toward both sides of heat exchanger 100 in a thickness direction (in a longitudinal direction of Fig. 4), the space of the installation of heat exchanger 100 is increased due to a portion protruding from the both sides of heat exchanger 100. Therefore, if heat exchanger 100 is used as a condenser for use in an automotive air conditioner, following problems may arise. For example, if such heat exchanger 100 is used as a condenser installed in an engine room of a vehicle, heat exchanger 100 and a radiator 105 are installed in the engine room in this order from the direction of an air flow direction as shown in an arrow A'.
  • an air flow route of air flowing radiator 105 after passing through heat exchanger 100 is lengthened.
  • a leakage of air between heat exchanger 100 and radiator 105 may arise. If the air between heat exchanger 100 and radiator 105 is leaked, the amount of air passing through radiator 105 may decrease.
  • a suction fan (not shown) disposed at the downstream of radiator 105 is activated, the amount of the air bypassing heat exchanger 100 and flowing directly to the radiator 105 may increase. As a result, the amount of the air passing through heat exchanger 100 may decrease.
  • a centre of a surface in a cross section of header pipe 102' is simply decentred toward an anti-radiator side in order to shorten the air flow route between heat exchanger 100 and radiator 105.
  • an inserting portion of each heat exchanger tube 103 into header pipe 102' is increased because the centre of a surface in a cross section of header pipe 102' is decentred.
  • each heat exchanger tube 103 and desiccant unit 104' may be interfered each other.
  • desiccant unit 104' e.g., a diameter of a surface in a cross section of desiccant unit 104
  • the function of removing water from refrigerant in desiccant 104' may be decreased.
  • a technical advantage of the present invention is to decrease a protruding portion of a header pipe from one side of the heat exchanger in a thickness direction, so that a radiator is disposed adjacent to the heat exchanger.
  • a further technical advantage of the present invention is to provide a heat exchanger preventing decrease of the amount of air passing through a radiator due to the air leakage between the heat exchanger and the radiator.
  • a heat exchanger comprises a first header pipe, second header pipe, a plurality of tubes, and a plurality of fins.
  • the first header pipe and a second header pipe are provided in a row arrangement.
  • the first header pipe has a desiccant member.
  • the plurality of tubes are provided in communication with the first header pipe and the second header pipe. Both end of each tube is inserted into the first header pipe and the second header pipe, respectively.
  • Each of the plurality of fins is disposed between said tubes.
  • a centre of cross-sectional area of the first header pipe is offset toward one side of the heat exchanger in an air flow direction, and an entire width of the end of each tube is inserted into the first header pipe, such that a clearance is created between the end of each tube and the desiccant member.
  • a heat exchanger according to a first embodiment is described.
  • the present invention applied to a condenser having a function as a receiver, in particular to a subcool-type condenser is described.
  • a subcool-type condenser 1 comprises a second header pipe 2, a first header pipe 3, and a plurality of heat exchanger tubes 4.
  • Second header pipe 2 and first header pipe 3 are vertically arranged in parallel with each other.
  • the plurality of heat exchanger tubes 4 extend in parallel with each other, communicating between header pipes 2 and 3.
  • Pluralities of corrugated fins 5 are provided between heat exchanger tubes 4 and on their outer layers.
  • Second header pipe 2 has an inlet pipe 6 for introducing refrigerant at an upper portion and an outlet pipe 7 for discharging the refrigerant at a lower portion in a vertical direction.
  • a partition plate 8 is provided within second header pipe 2.
  • Partition plate 8 divides the inside of second header pipe 2 into an upper compartment (an upper header pipe portion 2a) and a lower compartment (a lower header pipe portion 2b).
  • Partition plate 8 also divides the area, in which the plurality of heat exchanger tubes 4 are located, into a refrigerant condensing core 9 and a subcool core 10.
  • Refrigerant condensing core 9 condenses the refrigerant introduced into condenser 1.
  • Subcool core 10 supercools the condensed refrigerant from condensed refrigerant from refrigerant condensing core 9.
  • partition plate 8 provided in which second header pipe 2 is integrally formed divides the entire core of condenser 1 into refrigerant condensing core 9 and subcool core 10.
  • subcool-type condenser 1 there is a single refrigerant flow path formed of heat exchanger tubes 4 extending in parallel with each other in refrigerant condensing core 9. Therefore, the refrigerant introduced through inlet pipe 6 into second header pipe 2 passes through heat exchanger tubes 4 of refrigerant condensing core 9 constituting one path route, and flows into first header pipe 3. Subsequently, after the refrigerant flows downwardly within first header pipe 3, the refrigerant is directly introduced into an inlet of subcool core 10. Moreover, the refrigerant passes through each heat exchange tube 4 of subcool core 10, and flows out though outlet pipe 7.
  • refrigerant condensing core 9 may consist of two or more path routes.
  • an occupation rate of subcool core 9 to an entire subcool-type condenser 1 is set about 10%. According to an experiment implemented by the applicant, it is desirable that a range of this occupation rate is between about 5% and about 12%. By setting the occupation rate within this range, reducing the installation space for subcool-type condenser 1 in the engine room of the vehicle may be achieved. Moreover, an optimum supercool is achieved as well as an increase of the pressure at a high pressure side due to subcooling the refrigerant in a limited size of condensing area is suppressed and a deterioration of a fuel consumption of the vehicle is suppressed.
  • a portion at first header pipe 3 corresponding to the inlet of subcool core 10 is a liquid-refrigerant temporary retention portion 11.
  • the refrigerant from refrigerant condensing core 9, i.e., the refrigerant from an upper portion of first header pipe 3, is retained in retention portion 11. Subsequently, the refrigerant flows into each heat exchange tube 4 of subcool core 10 from retention portion 11.
  • first header pipe 3 in a thickness direction (the dimension of first header pipe 2 in a longitudinal direction in Fig. 2) is set larger than that of second header pipe 2.
  • a desiccant unit 13 filling a desiccant member 12 is inserted into first header pipe 3.
  • Desiccant unit 13 has a substantially C-shape in its cross section (not shown).
  • a lower portion of desiccant unit 13 is inserted into a strainer 14, which has a function capturing foreign materials.
  • desiccant unit 13 is accommodated within an entire length of first header pipe 3.
  • Desiccant unit 13 is supported by support members 15 and 16, which are disposed within first header pipe 3.
  • first header pipe 3 is disposed at a position downward of a thickness of subcool-type condenser 1 (downward in Fig. 2). Specifically, a centre of cross-sectional area of first header pipe 3 is offset toward an anti-radiator side. Moreover, a clearance is provided between an end portion of each heat exchange tube 4 inserted into first header pipe 3 and desiccant unit 13, so that interference between the end portion of each heat exchanger tube 4 and desiccant unit 13 is avoided.
  • a surface 18 substantially parallel with a heat exchanger surface 17 comprising the plurality heat exchange tubes 4 is formed at a circumferential surface of first header pipe 3.
  • first header pipe 3 is disposed at the position downward of a thickness of subcool-type condenser 1, i.e., toward an upstream of an air flow direction as shown in an arrow A. Specifically, the centre of cross-sectional area of first header pipe 3 is offset toward an anti-radiator side. Therefore, a protruding portion of first header pipe 3 toward radiator 19 may be considerably decreased, and the length of an air flow route between subcool-type condenser 1 and radiator 19 may be considerably shortened.
  • desiccant unit 13 is inserted within the entire length of first header pipe 3, so that the clearance is created between the end portion of each heat exchange tube 4 and desiccant unit 13. Therefore, interference between the end portion of each heat exchange tube 4 and desiccant unit 13 may be avoided.
  • a heat exchanger 20 (a subcool-type condenser 20) according to a second embodiment is described.
  • the same reference numbers are used to represent the same parts of heat exchanger 1 (subcool-type condenser 1) as shown in Figs. 1 and 2, and the explanation of the same parts is omitted.
  • a cross-sectional area of a first header pipe 21 of subcool-type condenser 20 has a substantially elliptical shape, which swells from an insert side of each heat exchanger tube 4 toward its axial end.
  • a centre of the cross-sectional area of first header pipe 21 is offset toward an anti-radiator side.
  • First header pipe 21 is disposed with an inclination to the anti-radiator side, so that a surface 22 of first header pipe 21 formed at its circumferential surface is substantially parallelled with a heat exchanger surface 17. Moreover, an entire width of an end portion of each heat exchange tube 4 is inserted within header pipe 21, such that the clearance is created between the end portion of each heat exchange tube 4 and a desiccant unit 13.
  • first header pipe 21 because the centre of the cross-sectional area of first header pipe 21 is offset toward an anti-radiator side, a protruding portion of first header pipe 21 toward a radiator 19 may be considerably decreased, and the length of an air flow route between subcool-type condenser 20 and radiator 19 may be considerably shortened. Moreover, because the clearance is created between the end portion of each heat exchanger tube 4 and a desiccant unit 13, interference between the end portion of each heat exchanger tube 4 and desiccant unit 13 may be avoided.
  • a length of an air flow route between a heat exchanger and a radiator is considerably shortened, a decrease of the amount of an air passing through the radiator may be avoided. Moreover, the space of the installation of the heat exchanger may be substantially reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP02258119A 2001-12-14 2002-11-26 Echangeur de chaleur Withdrawn EP1319907A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001381196 2001-12-14
JP2001381196A JP2003185296A (ja) 2001-12-14 2001-12-14 熱交換器

Publications (2)

Publication Number Publication Date
EP1319907A2 true EP1319907A2 (fr) 2003-06-18
EP1319907A3 EP1319907A3 (fr) 2003-07-02

Family

ID=19187303

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02258119A Withdrawn EP1319907A3 (fr) 2001-12-14 2002-11-26 Echangeur de chaleur

Country Status (3)

Country Link
EP (1) EP1319907A3 (fr)
JP (1) JP2003185296A (fr)
CN (1) CN1424550A (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2865026A1 (fr) * 2003-09-11 2005-07-15 Sanden Corp Echangeur de chaleur
EP1596146A2 (fr) * 2004-05-10 2005-11-16 Sanden Corporation Echangeurs de chaleur et systèmes de conditionnement d'air utilisant de tels échangeurs

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994011686A1 (fr) * 1992-11-18 1994-05-26 Behr Gmbh & Co. Condenseur pour l'installation de climatisation d'un vehicule
JPH07180930A (ja) * 1993-10-12 1995-07-18 Nippondenso Co Ltd 受液器一体型冷媒凝縮器
US5765633A (en) * 1996-03-25 1998-06-16 Valeo Thermique Moteur Condenser for a refrigerating circuit
FR2759447A1 (fr) * 1997-02-11 1998-08-14 Valeo Thermique Moteur Sa Condenseur a reservoir integre pour installation de climatisation, notamment de vehicule automobile
US5896754A (en) * 1995-06-23 1999-04-27 Valeo Thermique Moteur Condenser with built-in reservoir for motor vehicle air conditioning system
EP1104877A1 (fr) * 1999-12-01 2001-06-06 Visteon Global Technologies, Inc. Condenseur à réservoir dessiccateur intégré
US6267173B1 (en) * 1997-10-02 2001-07-31 Valeo Thermique Moteur Collection box with an integrated reservoir for a heat exchanger, in particular for a refrigeration condenser

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994011686A1 (fr) * 1992-11-18 1994-05-26 Behr Gmbh & Co. Condenseur pour l'installation de climatisation d'un vehicule
JPH07180930A (ja) * 1993-10-12 1995-07-18 Nippondenso Co Ltd 受液器一体型冷媒凝縮器
US5896754A (en) * 1995-06-23 1999-04-27 Valeo Thermique Moteur Condenser with built-in reservoir for motor vehicle air conditioning system
US5765633A (en) * 1996-03-25 1998-06-16 Valeo Thermique Moteur Condenser for a refrigerating circuit
FR2759447A1 (fr) * 1997-02-11 1998-08-14 Valeo Thermique Moteur Sa Condenseur a reservoir integre pour installation de climatisation, notamment de vehicule automobile
US6267173B1 (en) * 1997-10-02 2001-07-31 Valeo Thermique Moteur Collection box with an integrated reservoir for a heat exchanger, in particular for a refrigeration condenser
EP1104877A1 (fr) * 1999-12-01 2001-06-06 Visteon Global Technologies, Inc. Condenseur à réservoir dessiccateur intégré

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1995, no. 10, 30 November 1995 (1995-11-30) -& JP 07 180930 A (NIPPONDENSO CO LTD), 18 July 1995 (1995-07-18) *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2865026A1 (fr) * 2003-09-11 2005-07-15 Sanden Corp Echangeur de chaleur
EP1596146A2 (fr) * 2004-05-10 2005-11-16 Sanden Corporation Echangeurs de chaleur et systèmes de conditionnement d'air utilisant de tels échangeurs
EP1596146A3 (fr) * 2004-05-10 2006-11-02 Sanden Corporation Echangeurs de chaleur et systèmes de conditionnement d'air utilisant de tels échangeurs

Also Published As

Publication number Publication date
CN1424550A (zh) 2003-06-18
EP1319907A3 (fr) 2003-07-02
JP2003185296A (ja) 2003-07-03

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