US20080142190A1 - Heat exchanger for a vehicle - Google Patents

Heat exchanger for a vehicle Download PDF

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Publication number
US20080142190A1
US20080142190A1 US11/640,605 US64060506A US2008142190A1 US 20080142190 A1 US20080142190 A1 US 20080142190A1 US 64060506 A US64060506 A US 64060506A US 2008142190 A1 US2008142190 A1 US 2008142190A1
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United States
Prior art keywords
coolant
radiator
range
tube
flow
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.)
Abandoned
Application number
US11/640,605
Other languages
English (en)
Inventor
Sim Ho Chang
Jeong Sun An
Jun Gil Woong
Cho Byoung Sun
Lee Sang Yul
Jung Kwang Yong
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.)
Hanon Systems Corp
Original Assignee
Halla Climate Control 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 Halla Climate Control Corp filed Critical Halla Climate Control Corp
Priority to US11/640,605 priority Critical patent/US20080142190A1/en
Assigned to HALLA CLIMATE CONTROL CORP. reassignment HALLA CLIMATE CONTROL CORP. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHO, BYOUNG SUN, JEONG, SUN AN, JUN, GIL WOONG, JUNG, KWANG YONG, LEE, SAN YUL, SIM, HO CHANG
Priority to KR1020070123974A priority patent/KR101408899B1/ko
Priority to FR0759817A priority patent/FR2909939B1/fr
Priority to CN2007101608283A priority patent/CN101206099B/zh
Publication of US20080142190A1 publication Critical patent/US20080142190A1/en
Priority to US12/190,168 priority patent/US20090038562A1/en
Assigned to HALLA VISTEON CLIMATE CONTROL CORPORATION reassignment HALLA VISTEON CLIMATE CONTROL CORPORATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: HALLA CLIMATE CONTROL CORPORATION
Assigned to HANON SYSTEMS reassignment HANON SYSTEMS CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: HALLA VISTEON CLIMATE CONTROL CORPORATION
Abandoned legal-status Critical Current

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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
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F01P7/164—Controlling of coolant flow the coolant being liquid by thermostatic control by varying pump speed
    • 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
    • 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
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P2003/001—Cooling liquid
    • 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
    • F28D2021/0091—Radiators
    • F28D2021/0094—Radiators for recooling the engine coolant

Definitions

  • the present invention relates to a heat exchanger for a vehicle, and more particularly, to a highly efficient thin radiator for reducing production costs by decreasing the weight of a heat exchanger, reducing energy loss due to a pressure drop of a coolant-side in a case of being mounted in a real vehicle, and enhancing heat radiation performance.
  • FIG. 1 is a conceptual view showing a cooling system of a general vehicle. Since an engine 1 for a vehicle always ignites and burns high-temperature and high-pressure gas, the engine 1 is overheated in a case where it is left as it is, so that cylinders and pistons may be seriously damaged due to the melt of a metallic material constituting the engine 1 . In order to prevent this, as shown in FIG.
  • a water jacket (not shown), in which a coolant is stored, is mounted around the cylinder of the engine 1 for a vehicle, the engine is circularly cooled by allowing the coolant to pass through a radiator 2 or a heater core 3 using a water pump 5 , and the coolant may not pass through the heater core 3 but be immediately returned through a bypass circuit 6 depending on a use of cooling or heating.
  • the thermostat 4 is mounted in a path through which the coolant flows so as to function as an adjusting mechanism for preventing the engine 1 from being overheated by adjusting a degree of opening and shutting depending on a temperature of the coolant passing through the engine 1 .
  • FIG. 2 are a perspective view and an exploded perspective view of a general radiator, respectively.
  • the radiator is a kind of heat exchanger for allowing heat of the coolant to be radiated when the coolant receiving heat of the engine transferred while circulating to the engine flows.
  • the radiator is mounted to an engine room, and a cooling fan for blowing wind into the core of the engine is mounted to a central portion of the engine room.
  • the radiator is generally made of aluminum with a superior heat conduction effect, and has a characteristic in that heat radiation performance depends on elements of heat exchanging tubes and fins. That is, if the heights of the tube and the fin are reduced even in a radiator with the same core, the heat radiation performance is theoretically enhanced. However, if the height of the fin becomes too low, a foreign substance is stuck or stacked between the fins so that it interferes with ventilation, and since a foreign substance produced due to an antifreezing solution or a reactant is stacked inside the tube if the height of the tube becomes too small, there occurs a phenomenon in that a flow channel is blocked so that the deterioration of heat transfer performance may be rather caused. In this case, since the number of tubes and fins become large, there may be caused a problem in that this is very disadvantageous in a view of stability of a radiator structure and productivity in manufacturing.
  • the conventional radiator is focused on heat radiation performance of an outer side of the tube through which air passes. Further, in order to prevent a coolant-side pressure drop, the caliber of the tube is set not to be small, and the height of the fin is simultaneously set to be relatively high considering an air-side pressure drop amount.
  • coolant-side pressure drop amount is not simultaneously considered together with air-side heat radiation performance.
  • a preferred design object of exchanger tubes in a critical operation condition such as alpine regions with many inclines or cold or arctic regions.
  • a heat exchanger for a vehicle for exchanging heat between a coolant heated by an engine and air flowed into the front of the vehicle to cool the engine including: a pair of tanks for supplying a coolant supplied from the engine through a thermostat for adjusting opening/shutting depending on the temperature of the coolant and a water pump, and discharging the cooled coolant to an engine side; a core portion including a header at one side coupled with the tank at one side, to which the coolant is supplied, heat exchange tubes which is structurally fastened to communicate with the heater at one end portion thereof, and arranged in parallel to a direction of driving wind, a header at the other side coupled with the tank at the other side, which is structurally fastened at the other end portion of the heat exchange tube to communicate therewith so as to discharge the coolant into the engine, and fins fixedly brazed between the heat exchange tubes; wherein Td the width of a core of the heat exchanger is in the range of 12 to 15 mm, the
  • the flow rate of the coolant when the flow rate of the coolant is in the range of 60 to 80 L/min and the temperature thereof is 100° C., the flow of the coolant has a Reynolds number of 2,100 or more, a transition from laminar flow to turbulent flow occurs at a flow rate of 40 L/min or less.
  • the pressure drop amount of the coolant at an exit side of the heat exchanger is 150 mmHg.
  • Th the outer width of the tube is in the range of 1.60 to 2.10 mm, and more preferably, 1.70 to 1.90 mm.
  • Tth the material thickness of the tube is in the range of 0.15 to 0.24 mm for the purpose of reducing a weight and a pressure drop amount.
  • the height of the fin is in the range of 5.3 to 5.8 mm, and the thickness of the fin is in the range of 0.05 to 0.06 mm for the purpose of reducing a weight and maximizing a heat transfer rate.
  • the heat exchange tube is a flat type with no dimple in an interior thereof, and the heat exchanger is a cross flow type.
  • FIG. 1 is a conceptual view showing a cooling system of a general vehicle.
  • FIG. 2 are a perspective view and an exploded perspective view of a down flow type radiator that is a general heat exchanger, respectively.
  • FIG. 3 are a perspective view and an exploded perspective view of a cross flow type radiator that is a general heat exchanger, respectively.
  • FIG. 4 is a graph illustrating characteristics of heat radiation and pressure drop of radiators according to the present invention and prior arts.
  • FIG. 5 is an enlarged perspective view showing a coupling feature of a tube and a fin in the radiator.
  • FIG. 6 is a graph illustrating a change in heat transfer rate and pressure drop of the radiator depending on the height of the fin in the present invention.
  • FIG. 7 is a graph illustrating a change in heat transfer rate pressure drop of the radiator depending on the outer width of the tube in the present invention.
  • FIG. 8 is a graph illustrating a change in heat transfer rate and pressure drop of the radiator depending on the material thickness of the tube in the present invention.
  • a plurality of tubes constituting a radiator are generally formed as a duct with a flat shape, the flow of a coolant flowing into the tube can be classified into a duct flow which is not opened.
  • a main cause is a Reynolds number. In a circular duct, if a Reynolds number reach about 2,300, a flow generally starts forming a “mass” or “puff” and approaching a region of a turbulent flow.
  • a condition of pressure loss should be considered as well as a condition of a turbulent flow in a tube.
  • the aforementioned pressure loss may be divided into an influence by elements of a heat exchanger and a tube and an influence by a property of a flow.
  • a turbulent flow condition of the flow of a coolant flowing into a heat exchange tube and the influence of pressure loss are simultaneously considered to enhance such a heat radiation characteristic of a heat exchanger itself, so that there can be provided design elements of the heat exchanger for a more effective cooling system.
  • a radiator of the present invention can be applied to both a down flow type in which heat exchange tubes are arranged in a vertical direction as shown in (a) and (b) of FIG. 2 and a cross flow type in which heat exchange tubes arranged in a horizontal direction as shown in (a) and (b) of FIG. 3 .
  • the radiator of the present invention can perform superior performance in a cross flow type heat exchanger in which a flow speed in the tube is relatively fast.
  • FIG. 4 is a graph illustrating characteristics of heat radiation and pressure drop of radiators according to the present invention and prior arts.
  • Prior arts A and B show heat radiation characteristics and pressure drop characteristics for two kinds of existing radiators, respectively.
  • the composition of an antifreezing solution and water is 1:1 in a coolant flowing into a core portion, the temperature of the coolant is 100° C., the temperature of inflow air is 40° C., and the front area of the same core is 636 ⁇ 485.
  • the radiator according to the present invention is set such that Td the width of a core is in the range of 12 to 15 mm and the height thereof is in the range of 300 to 600 mm.
  • the reason why Td the width of the core is limited as within the range of 12 to 15 mm is that the component package of the radiator can be minimized and air-side pressure drop can be lowered. Further, the thickness of a fin is set to be in the range of 0.05 to 0.06 mm so that the increase of the entire weight of the radiator can be prevented and the heat transfer rate can be maximized.
  • the radiator according to the present invention has an advantage in that a driving region with a coolant flow rate from 60 to 80 L/min is set as a major interval in critical and real driving conditions including a hill-climbing mode so that heat radiation performance in a region including the driving region can be enhanced and a pressure drop amount can be reduced.
  • the pressure drop characteristic is satisfactory, but a transition starts from a point at which an inflection point of the graph exists near a coolant flow rate of 60 L/min in a case of the existing radiator A. That is, it can be seen that, since a transition occurs from a laminar flow to a turbulent flow in a region of a coolant flow rate from 60 to 80 L/min that is an interesting region of the present invention, a turbulent flow region which is not completely developed is formed. Thus, since such a transition region is formed near a coolant flow rate of 60 L/min, heat radiation performance of the existing radiator A is lowered as compared with the present invention.
  • the reason why the heat radiation characteristic of the existing radiator A is lowered under the aforementioned condition is that although the width of a tube is lager as compared to the present invention such that a much amount of the coolant flows, but causing delay in transition of a turbulent flow. That is, since a much amount of the coolant flows, a heat transfer rate is identical with or larger than the present invention in an interval except 60 to 80 L/min, but the heat transfer rate is lowered as compared with the present invention due to the existence of the transition region in the range of 60 to 80 L/min.
  • the present invention can maintain a width narrower than conventional radiators, and perform relatively superior performance to conventional thick radiators in a range of 60 to 80 L/min which is a critical driving region.
  • a completely developed turbulent flow region is formed in a region of a coolant flow rate from 60 to 80 L/min, and a pressure drop characteristic also has a satisfactory distribution in a case of the radiator according to the present invention.
  • the radiator of the present invention is designed such that a transition occurs in a region of a coolant flow rate of 40 L/min or less.
  • the radiator of the present invention is configured such that a completely developed turbulent flow region is formed in a region of a coolant flow rate from 60 to 80 L/min, which is an important region for a critical driving condition, and the pressure drop amount in the aforementioned region maintains 150 mmHg or less.
  • FIG. 5 is an enlarged perspective view showing a coupling feature of a tube and a fin in the radiator.
  • b is the inner width of the tube
  • Td is the outer height of the tube, which corresponds to the width of a core portion.
  • FIG. 6 is a graph illustrating a change in heat transfer rate pressure drop of the radiator depending on height Fh of the fin with respect to a case where height Th is respectively 1.60 mm, 1.80 mm and 2.10 mm in the present invention.
  • Q heat transfer rate of the radiator
  • Q 0 is a minimum required heat transfer rate of the radiator for cooling the engine.
  • the left vertical axis is Q/Q 0 value showing a minimum required heat transfer rate
  • the right vertical axis shows a coolant-side pressure drop amount.
  • the solid line of the graph indicates a heat transfer rate ratio
  • the dotted line indicates a coolant-side pressure drop amount.
  • Fh Height of the fin in the present invention can be set to have a preferred range from the graph of FIG. 6 .
  • Fh height of the fin is set to be 5.3 mm ⁇ Fh ⁇ 5.8 mm as a preferred region within a range where the heat transfer rate is maintained as a sufficiently high value and the pressure loss in the tube is not rapidly increased with reference to the required condition and the characteristic of FIG. 6 .
  • FIG. 7 is a graph illustrating a change in heat transfer rate pressure loss of the radiator depending on Th height of the tube when Fh height of the fin is respectively 5.3 mm, 5.5 mm and 5.8 mm in the present invention.
  • Th Height of the tube of the radiator of the present invention can be set to have a preferred range from the graph of FIG. 7 . That is, there is a problem in that, in a case where Th height of the tube exceeds 2.10 mm, a coolant flowing in the tube is difficult to become turbulent flow so that the heat transfer rate is dropped below the minimum required heat transfer rate, and an additional process of forming a means for accelerating a turbulent flow, such as a dimple in the tube, should be added to satisfy a required heat transfer rate.
  • Th the height of the tube is set to be preferably 1.60 mm ⁇ Th ⁇ 2.10 mm, and more preferably 1.70 mm ⁇ Th ⁇ 1.90 mm, as a range where the heat transfer rate is maintained as a sufficiently high value and the pressure loss in the tube is not rapidly increased with reference to the required condition and the characteristic of FIG. 7 .
  • FIG. 8 is a graph illustrating a change in heat transfer rate and pressure drop of the radiator depending on Tth thickness of the tube in the present invention.
  • Tth The thickness of the tube in the radiator of the present invention is set to have a preferred range from the graph of FIG. 8 . That is, there is a problem in that, as Th thickness of the tube becomes thick, the weight of the radiator is increased and the coolant-side pressure drop amount is largely increased so that excessive power is required to circulate the coolant.
  • Tth thickness of the tube is set to be preferably 0.15 mm ⁇ Tth ⁇ 0.24 mm as a range where the heat transfer rate is maintained as a sufficiently high value and the pressure drop in the tube is not rapidly increased with reference to the required condition and the characteristic of FIG. 8 .
  • the radiator of the present invention is a thin radiator for reducing the weight of a heat exchanger, enhancing heat radiation performance and reducing a pressure drop amount, and has advantages such as lightweight of a vehicle, increase of fuel efficiency and setting for a layout of a vehicle.
  • the radiator according to the present invention has an advantage in that heat radiation performance can be enhanced in a driving region of a coolant flow rate from 60 to 80 L/min, which is a critical driving condition of a vehicle including a hill-climbing mode, and a pressure drop amount can be reduced.
  • the present invention has an advantage in that there is suggested an optimal design range in which the heat radiation characteristic and pressure drop amount of the radiator can be mutually complemented.
  • the thickness of a core is set to be thin in view of a cooling system so that an interval with a cooling fan can be more separated, thereby enhancing air-side efficiency.
US11/640,605 2006-12-18 2006-12-18 Heat exchanger for a vehicle Abandoned US20080142190A1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US11/640,605 US20080142190A1 (en) 2006-12-18 2006-12-18 Heat exchanger for a vehicle
KR1020070123974A KR101408899B1 (ko) 2006-12-18 2007-11-30 차량용 열교환기
FR0759817A FR2909939B1 (fr) 2006-12-18 2007-12-13 Echangeur de chaleur pour un vehicule
CN2007101608283A CN101206099B (zh) 2006-12-18 2007-12-18 车用热交换器
US12/190,168 US20090038562A1 (en) 2006-12-18 2008-08-12 Cooling system for a vehicle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/640,605 US20080142190A1 (en) 2006-12-18 2006-12-18 Heat exchanger for a vehicle

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US12/190,168 Continuation-In-Part US20090038562A1 (en) 2006-12-18 2008-08-12 Cooling system for a vehicle

Publications (1)

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US20080142190A1 true US20080142190A1 (en) 2008-06-19

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US11/640,605 Abandoned US20080142190A1 (en) 2006-12-18 2006-12-18 Heat exchanger for a vehicle

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US (1) US20080142190A1 (zh)
KR (1) KR101408899B1 (zh)
CN (1) CN101206099B (zh)
FR (1) FR2909939B1 (zh)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090239106A1 (en) * 2008-03-24 2009-09-24 Whitehead Lee C Integrated charge air heat exchanger
US20100243208A1 (en) * 2009-03-17 2010-09-30 Kar Kishore K Tube-side sequentially pulsable-flow shell-and-tube heat exchanger appratus, system, and method
US20100262301A1 (en) * 2009-04-10 2010-10-14 William Samuel Schwartz Method for controlling heat exchanger fluid flow
US20130070453A1 (en) * 2010-05-31 2013-03-21 NEC DIsplaay Solutions, Ltd. Display device

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KR101250753B1 (ko) * 2010-06-17 2013-04-04 한라공조주식회사 라디에이터
JP6028815B2 (ja) * 2015-01-19 2016-11-24 ダイキン工業株式会社 空気調和装置の熱交換ユニット
CN105041452A (zh) * 2015-08-06 2015-11-11 力帆实业(集团)股份有限公司 摩托车水冷系统散热器及其散热结构
CN105041451A (zh) * 2015-08-06 2015-11-11 力帆实业(集团)股份有限公司 摩托车散热器结构

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US2252211A (en) * 1939-10-18 1941-08-12 Mccord Radiator & Mfg Co Heat exchange core
US4119144A (en) * 1975-11-24 1978-10-10 Union Carbide Corporation Improved heat exchanger headering arrangement
US4332293A (en) * 1980-04-30 1982-06-01 Nippondenso Co., Ltd. Corrugated fin type heat exchanger
US4558695A (en) * 1982-07-02 1985-12-17 Nippondenso Co., Ltd. Method of manufacturing a heat exchanger
US4693307A (en) * 1985-09-16 1987-09-15 General Motors Corporation Tube and fin heat exchanger with hybrid heat transfer fin arrangement
US5076354A (en) * 1989-04-26 1991-12-31 Diesel Kiki Co., Ltd. Multiflow type condenser for car air conditioner
US5311935A (en) * 1992-01-17 1994-05-17 Nippondenso Co., Ltd. Corrugated fin type heat exchanger
US5329988A (en) * 1993-05-28 1994-07-19 The Allen Group, Inc. Heat exchanger
US5564497A (en) * 1994-11-04 1996-10-15 Nippondenso Co., Ltd. Corrugated fin type head exchanger
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Publication number Priority date Publication date Assignee Title
US20090239106A1 (en) * 2008-03-24 2009-09-24 Whitehead Lee C Integrated charge air heat exchanger
US8057946B2 (en) * 2008-03-24 2011-11-15 GM Global Technology Operations LLC Integrated charge air heat exchanger
US20100243208A1 (en) * 2009-03-17 2010-09-30 Kar Kishore K Tube-side sequentially pulsable-flow shell-and-tube heat exchanger appratus, system, and method
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FR2909939B1 (fr) 2015-10-30
CN101206099B (zh) 2010-06-16
KR101408899B1 (ko) 2014-06-18
FR2909939A1 (fr) 2008-06-20
CN101206099A (zh) 2008-06-25
KR20080056640A (ko) 2008-06-23

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