[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

LU101721B1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

Info

Publication number
LU101721B1
LU101721B1 LU101721A LU101721A LU101721B1 LU 101721 B1 LU101721 B1 LU 101721B1 LU 101721 A LU101721 A LU 101721A LU 101721 A LU101721 A LU 101721A LU 101721 B1 LU101721 B1 LU 101721B1
Authority
LU
Luxembourg
Prior art keywords
header plate
heat exchanger
collar
wall thickness
bulge
Prior art date
Application number
LU101721A
Other languages
French (fr)
Inventor
Thierry Berger
Chris Calhoun
Richard Cipriano
Hervé Damotte
Vincent Nautet
Original Assignee
Ht Holding Luxembourg S A
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 Ht Holding Luxembourg S A filed Critical Ht Holding Luxembourg S A
Priority to LU101721A priority Critical patent/LU101721B1/en
Application granted granted Critical
Publication of LU101721B1 publication Critical patent/LU101721B1/en

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02Header boxes; End plates
    • F28F9/0219Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0224Header boxes formed by sealing end plates into covers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02Header boxes; End plates
    • F28F9/04Arrangements for sealing elements into header boxes or end plates
    • F28F9/16Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
    • F28F9/18Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
    • F28F9/182Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding the heat-exchange conduits having ends with a particular shape, e.g. deformed; the heat-exchange conduits or end plates having supplementary joining means, e.g. abutments
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00Reinforcing means
    • F28F2225/04Reinforcing means for conduits
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00Reinforcing means
    • F28F2225/08Reinforcing means for header boxes
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00Fastening; Joining
    • F28F2275/04Fastening; Joining by brazing

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)

Abstract

A heat exchanger comprises a plurality of flat tubes (12) for conveying a fluid; a tank (14) to which the flat tubes are fluidly connected; and at least one header plate (16) closing said tank. The header plate has oblong apertures (22) receiving ends of the tubes inserted along an insertion direction, wherein the header plate is configured so that each oblong aperture is surrounded by a collar (24) to which a respective tube end is fixed by brazing. For at least some of the oblong apertures, the collar is connected to the header plate by means of an annular bulge (26) protruding from the front side of the header plate, wherein said annular bulge is formed by plastic deformation of the header plate and comprises an outer branch (28) joining with the header plate and an inner branch (30) joining the corresponding collar (24), the annular bulge being elastically deformable to absorb displacement along said insertion direction. The inner branch (30) has a generally smaller wall thickness than the outer branch (28).

Description

1 LU101721 |
Heat exchanger |
FIELD OF THE INVENTION |
The present invention generally relates to the field of heat exchangers and | particularly relates to fluid-air heat exchangers as arranged in automotive É vehicles. | BACKGROUND OF THE INVENTION |
A heat exchanger such as a radiator, condenser or evaporator, for use in an ; automotive vehicle typically includes an inlet tank, an outlet tank and a plurality a of flat tubes extending between the tanks and hydraulically connecting the tanks | for fluid flow there between.
The connection of the tubes at each header is done É by means of a header plate comprising oblong apertures in which the tubes are | engaged.
External fins are provided on the tubes to increase heat transfer to | ambient air.
The tanks, header plates, tubes and fins are typically assembled 0 into a unitary structure and brazed. (
As is known, a first heat transfer fluid, e.g. a liquid coolant or a two-phase El refrigerant, flows from the inlet tank to the outlet tank through the plurality of | tubes.
The first heat transfer fluid is in contact with the interior surfaces of the 0 tubes while a second heat transfer fluid, such as ambient air, is in contact with | the exterior surfaces of the tubes and fins.
Where a temperature difference A exists between the first and second fluids, heat is transferred from the higher 2 temperature fluid to the lower temperature fluid through the walls of the tubes. fi
In operation, the heat exchanger is subject to heat load variations (hot / cold ; cycling), causing high thermal stresses on the radiator tubes.
This leads to the |, development of cracks at the tubes — header plate junction, which propagate | within the brazed structure and leads to radiator leakages. | In order to improve the robustness of the tubes without increasing their wall | thickness (which would significantly increase the weight of the heat exchanger), | it has been proposed to use reinforcement clamps that are inserted inside the | tubes at the junction between the tubes and header plate.
Such clamps are |
2 LU101721 ; engaged in the tube ends, at specific locations, from the inner side of the A header plate, to reinforce the edges (nose) of the tube. ;
An example of such clamps is e.g. disclosed in US 2007/131404. | Another known approach for reinforcing the tube junction is known as “double 0 heather plate” and shown e.g. in FR 2 770 632. The header plate has a plurality | of oblong openings for receiving the ends of the tubes.
An insert plate, with the | same number of oblong openings, is fixed against the outer side of the header - plate.
The openings in the insert plate are surrounded by peripheral walls that | engage into the openings in the header plate, and which receive the ends of the ,
tubes.
The peripheral walls are in contact with the whole outer periphery of the | tubes to which they are brazed. | OBJECT OF THE INVENTION |
The object of the present invention is to provide an improved heat exchanger of | a robust design. 2
This object is achieved by a heat exchanger as claimed in claim 1. | SUMMARY OF THE INVENTION ; According to the invention, a heat exchanger comprises: | a plurality of flat tubes for conveying a fluid; | a tank to which the flat tubes are fluidly connected; :
at least one header plate closing the tank, the header plate having a rear side, | facing the inner volume of the tank, and an opposite front side, and comprising | oblong apertures receiving ends of the tubes inserted along an insertion | direction, wherein the header plate is configured so that each oblong aperture is | surrounded by a collar to which a respective tube end is fixed by brazing: | wherein for at least some of the oblong apertures, the collar is connected to the / header plate by means of an annular bulge protruding from the front side of the | header plate, wherein the annular bulge is formed by plastic deformation of the à header plate and comprises an outer branch joining with the header plate and |
3 LU101721 | an inner branch joining the corresponding collar, the annular bulge being : elastically deformable to absorb displacement along the insertion direction; and ; wherein the inner branch has a generally smaller wall thickness than the outer | branch. ; In the present design, the header plate has oblong openings where the tube | ends are conventionally fixed by means of a collar (peripheral wall). It should : however be appreciated that the collar is indirectly connected to the header ; plate body by means of an annular bulge that is obtained by plastic deformation, ; preferably by punching. This annular bulge acts as a spring that allows thermal | expansion of the tube in the insertion direction. Hence, the spring — bulge É absorbs the deflection instead of allowing deformation, and thus stress, to be ; transferred to the tubes. | The bulge may be formed as a generally U-shaped annular bend. ’ In embodiments, the wall thickness of the bulge decreases progressively, in a | stepped or (partially-) continuous manner, from the outer branch t&o the inner fi branch. Ë In embodiments, the inner branch is bent to define a funnel-shaped inlet section .
that extends from the front side of the header plate to the rear side and ends | with the collar; and wherein the wall thickness of the inner branch transitions | smoothly with the collar. | In embodiments, the wall thickness at the front-most part of the bulge is | between 70 and 40% of the header plate nominal wall thickness, preferably | between 50 and 60%. | In embodiments, the wall thickness at the inner section is between 20 and 45% | of the header plate nominal wall thickness, preferably between 30 and 40%. | In embodiments, the collars have a length, along the insertion direction, of at | least 2, 3 or 4 times the header plate nominal wall thickness. | The header plate may have a thickness of about 1 to 2 mm, in particular 1 to |
4 LU101721 ; Conventionally, the collar is obtained by plastic deformation of the header plate, together with the bulge. / The said bulge and collar are preferably obtained by punching. j BRIEF DESCRIPTION OF THE DRAWINGS ‘ The present invention will now be described, by way of example, with reference ; to the accompanying drawings, in which: | Fig. 1: is a perspective view of a tube connected to a tank according to an — embodiment of the present heat exchanger; A Fig. 2: is a vertical cross-section view of Fig.1, in a direction perpendicular to | the header plate; .
Fig. 3: is a section view though the header plate assembly; and / Fig. 4: is a perspective view of the header plate; and .
Fig. 5: is a perspective view of the header plate. ; DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS ; In reference to Fig.1, a fluid-air heat exchanger 10 according to an embodiment | of the invention is presented, for application in an automotive vehicle. The heat ] exchanger 10 comprises a plurality of tubes 12 (only one is shown) extending | beiween opposite tanks 14 (only one is shown, partially). | The tubes 12 are substantially straight and comprise one or more internal | channels for the flow of a heat transfer fluid. To improve thermal transfer, heat | exchange elements, e.g. corrugated fins (not shown), are conventionally fixed | onto the outer surfaces of the tubes. | In the shown embodiment the tubes 12 are flat and have a generally rounded- | off rectangular cross-section. Each tube 12 thus has two opposite broad sides |
12.1 in the thickness direction of the tube and two opposite nose-forming | narrow sides 12.2 in the width direction of the tube.
5 LU101721 / The tubes 12 are made from one or more folded metal sheet strips, e.g. / aluminum sheet.
In the shown embodiment the tubes 12 are each made from a | single metal sheet strip folded in B-form, thus defining two internal channels. | The longitudinal edges of the strip are joined in the middle of a broad side 12.1, whereby the tube is substantially symmetrical and the two channels have the | same flow cross-section.
This is only an example and other flat tube designs | may be used. : The tubes 12 are arranged in a parallel and aligned manner, to form a single / row.
Other configurations are however possible. | At both ends, the tubes 12 are in fluid communication with a respective tank 14. / Each tank 14 has a body defining a cavity that is closed by a plate 16 referred ; to as header plate.
The header plate 16 has an inner side 18 facing the inside of ; the tank 14 and an opposite outer side 20. | The tubes 12 are connected to the tanks 14 at their ends, which are engaged | into oblong apertures 22 in the header plates 16. Hence, all of the tubes 12 / open into the tanks 14 through a respective aperture 22 in the header plate 16. The header plate 16 is a plate-like element of generally rectangular shape that : is made using a deformation process, such as punching (generally ) metalworking). The header plate 16 extends along a longitudinal axis L.
The | oblong apertures 22 are operated across the width of the header plate 16 and | namely extend substantially perpendicularly to axis L.
The tubes 12 are inserted | into the oblong apertures 22 along an insertion direction (arrow in Fig.2) that is | generally perpendicular to the plane of the header plate 16. | As will be understood from Fig. 2, the header plate 16 is configured so that each ) oblong aperture 22 is surrounded by a collar 24, obtained by plastic deformation | of the header plate 16, to which a respective tube end is fixed by brazing.
The | collar 24, which may also be referred to as sleeve or peripheral wall, exiends away from the header plate 16, towards the inside of the tank 14. The collar 24 | is connected to the header plate 16 by means of an annular bulge 26 protruding | 30 from the front side 20 of the header plate 16. The annular bulge 26 is obtained by plastic deformation of the header plate 16 (e.g. punching / metalworking) and YY ggg EE
6 LU101721 | comprises an outer section or branch 28 connecting and integral with the plate | 16 and an inner section or branch 30 connecting with the collar 24. The annular | bulge 26 forms an oblong protrusion surrounding the oblong aperture 22. | The collar 24 has a length, Lc, in insertion direction, which is typically greater | than that nominal wall thickness f, (or gage) of the header plate 16, which | allows for a good attachment/binding to the tube ends by brazing. This ensure a | strong connection and with proper sealing. .
The annular bulge 26 forms a kind of double spring that allows some | displacement in the insertion direction. The annular bulge 26 permits absorbing É and distributing the stress due to thermal cycles: a tube 12 is allowed to expand | axially without constraint from the adjacent tube, e.g. during mal-flow | distribution (and consequently non uniform temperature distribution). : Since the annular bulge 26 is formed by plastic deformation of the header plate _ 16 it does not correspond to a local thickness reinforcement. To the contrary, É the wall thickness of the annular bulge 26 is not greater than the nominal wall © thickness, f,, of the header plate. For conventional radiators, the header plate .
16 may have a nominal thickness f, of about 1 to 2 mm, in particular between 1 — and 1.5 mm. 0 The bulge 26 has a generally convex shape. As indicated, it is obtained by | metalworking (punching) and is thus formed as a generally U-shaped annular | bend (or fold) having an oblong shape homologous to the sleeve 24. . Accordingly, the bulge’s U-shaped profile comprises the inner and outer | branches 28, 30 and a possibly central branch 32 forming the front-most portion | of the bulge 26. The outer and inner branches 28, 30 may be siraight or curved. | The central branch 32 may be flat or curved. The central branch 32 is desirable | to give certain spacing between the inner and outer branches 28, 30 along axis | L. However the central branch 32 can be very short, or omitted, whereby the . inner and outer branches 28, 30 are shaped to form a U. | As can be seen in Fig.2, the inner branch 30 is bent to define a funnel-shaped | inlet section that extends from the front side 20 of the header plate 16 to its rear | side 18 and ends with the collar 14. |
It shall further be appreciated that the wall thickness of the bulge 26 is designed | to taper throughout the bulge 26, from the outer branch 28 to the inner branch |
30. As can be seen in Fig.2, the wall thickness of the bulge 26 progressively L decreases from the junction plate 16 - outer branch 28, up to the end of the | inner branch 30 connecting the collar 24. The taper (decrease in wall thickness) | is here progressive and continuous, i.e. without steps. .
The inner branch 30 advantageously ends with a terminal section that is straight 0 and aligned with the insertion direction, connecting the collar 24. The wall . thickness of the inner branch 30 transitions smoothly with the collar 24. The .
collar may have a constant wall thickness. However, in consideration of the | punching process, the collar may also have a thickness decreasing along the - insertion direction. | In practice, the bulge and collar can be formed by punching with a progressive | die, whereby a progressive decrease in thickness can be controlled, from the | junction to the plate body up to the end of the collar. 0 At the central branch 32, the thickness £ may correspond to between 70 and | 40% of the nominal wall thickness f,, preferably between 50 and 60% . The wall | thickness £ at the terminal section of the inner branch 30, i.e. at the junction with | collar 24, may be between 20 and 45% of the plate’s nominal wall thickness £,, | preferably between 30 and 40%. | The bulge 26 is preferably configured so that the central branch 32 protrudes x from a predetermined distance from the header plate’s front side 20. The . foremost part of the bulge 26 may, e.g., be at a distance dr that corresponds to | about 80% to 200% of the nominal thickness £,. That is: 0.8*t, < d; < 2* tb. | More preferably, the distance dris comprised in the range 1.3*f, to 2%. © As indicated above, the header plate is typically a punched component; hence | the bulge 26 and collar 24 are integrally formed with the header plate 16. 2 The collar 24 typically has a length, in insertion direction, which is a multiple of 3 the nominal wall thickness. For example, the length Le of the collar may be | between 1.5 and 4 times the nominal thickness t,, in particular between 2 and 3. .
8 LU101721 ) it remains to be noted that in Figs.1 and 2 an integral mounting frame 21 . surrounds the header plate 16 and is configured for assembly to the tank 14. .
The header plate 16 and mounting frame 21 are thus made in one piece. The 0 mounting frame is designed as a protruding U-shaped rim that engages the 0 outer edge of the tank 14, as seen in Fig. 2. A number of crimping tabs 23 : extend at the rear of the mounting frame 21, which are bent against the tank 14. 0 Figs. 3 to 5 relate to an embodiment of the invention where the header plate 16’ | is combined with a separate mounting frame 32, forming a header plate Ë assembly 34. The header plate 16’ is here of simple planar shape, but includes 0 oblong openings 22 with bulge 26 and collar 24 of same/similar design as in ; Fig. 2. The mounting frame 32 has a rectangular shape with two longitudinal Ë members 32.1 and two transverse members 32.2. The members 32.1 and 32.2 2 have a corner profile. The header plate 16’ is arranged such that the peripheral . edge of the rear side 20 is against members 32.1 and 32.2 of the mounting | frame 32. More precisely, a peripheral shoulder 33 is provided at the inner edge 3] of the rectangular frame 32, against which the header plate 16’ is arranged. The ; thicknesses are selected such that the outer side 20 of the header plate 16’ lies | flush with the mounting frame 32. | During brazing, a peripheral seal will form between the header plate 16 and | mounting frame 32. A number of mounting features 34, e.g. crimping tabs, are | provided on the mounting frame 32 for attachment to the tank 14. A number of | transverse elements 36 (optional) are provided for reinforcement. The mounting | frame 32 is manufactured by punching, and is thus an integral piece. 0 For brazing purposes, the header plate 16’ is provided on one side 20 with a / cladding layer. The cladding layer also extends to the collars 24 and bulges 26. | Accordingly, the collars sides facing the ends of the tubes 12 are covered with Ë cladding material. The collars 24 have a smooth and flat surface, with a cross- 2 section matching the outer section of the tubes so that there is a tight fit. The . outer surface of the tube ends is also flat and smooth. | Any appropriate cladding material can be used, e.g. an aluminum brazing alloy É from the series AAAXXX. ;

Claims (12)

Claims
1. À heat exchanger comprising: a plurality of flat tubes (12) for conveying a fluid; a tank (14) to which said flat tubes are fluidly connected; at least one header plate (16) closing said tank, said header plate having a rear side (18), facing the inner volume of the tank, and an opposite front side (20), and comprising oblong apertures (22) receiving ends of said tubes inserted along an insertion direction, wherein the header plate is configured so that each oblong aperture is surrounded by a collar (24) to which a respective tube end is fixed by brazing; wherein for at least some of said oblong apertures, the collar is connected to the header plate by means of an annular bulge (26) protruding from the front | side of the header plate, wherein said annular bulge is formed by plastic | deformation of the header plate and comprises an outer branch (28) joining | with the header plate and an inner branch (30) joining the corresponding | collar (24), said annular bulge being elastically deformable to absorb 1 displacement along said insertion direction; and | wherein said inner branch (30) has a generally smaller wall thickness than said outer branch (28). |
2. The heat exchanger as claimed in claim 1, wherein inner branch (30) is bent ) to define a funnel-shaped inlet section that extends from the front side of the | header plate to the rear side and ends with the collar; and wherein the wall | thickness of the inner branch transitions smoothly with the collar. |
3. The heat exchanger as claimed in claim 1 or 2, wherein said bulge (26) is | formed as a generally U-shaped annular bend. |
4. The heat exchanger as claimed in claim 1, 2 or 3, wherein the wall thickness | of said bulge (26) progressively decreases, in a stepped or continuous manner, from the outer branch to the inner branch. |
5. The heat exchanger as claimed in any one of the preceding claims, wherein | the wall thickness at the front-most part of the bulge (26) is between 70 and ee SE
40% of the header plate nominal wall thickness, preferably between 50 and 60%.
6. The heat exchanger as claimed in any one of the preceding claims, wherein the wall thickness at the inner section is between 20 and 45% of the header plate nominal wall thickness, preferably between 30 and 40%.
7. The heat exchanger as claimed in any one of the preceding claims, wherein the collars (24) have a length, along said insertion direction, of at least 2, 3 | or 4 times the header plate nominal wall thickness. | ;
8. The heat exchanger as claimed in any one of the preceding claims, wherein | the header plate has a nominal wall thickness of about 1 to 2 mm, in | particular 1 to 1.5 mm. |
9. The heat exchanger as claimed in any one of the preceding claims, wherein | said collar is obtained by plastic deformation of said header plate. |
10. The heat exchanger as claimed in any one of the preceding claims, wherein | said bulge and collar are obtained by punching. |
11. The heat exchanger as claimed in any one of the preceding claims, wherein | an integral mounting frame (21) surrounds the header plate (16) and is L configured for assembly to the tank (14). |
12.The heat exchanger as claimed in any one of claims 1 to 10, wherein the | header plate (16°) is combined with a separate rectangular mounting frame ; (32), preferably fixed thereto by brazing. . _— III
LU101721A 2020-03-31 2020-03-31 Heat exchanger LU101721B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
LU101721A LU101721B1 (en) 2020-03-31 2020-03-31 Heat exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
LU101721A LU101721B1 (en) 2020-03-31 2020-03-31 Heat exchanger

Publications (1)

Publication Number Publication Date
LU101721B1 true LU101721B1 (en) 2021-09-30

Family

ID=70334009

Family Applications (1)

Application Number Title Priority Date Filing Date
LU101721A LU101721B1 (en) 2020-03-31 2020-03-31 Heat exchanger

Country Status (1)

Country Link
LU (1) LU101721B1 (en)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4316503A (en) * 1979-10-12 1982-02-23 Nippondenso Co., Ltd. Solderless heat exchanger
US4360060A (en) * 1980-06-05 1982-11-23 Valeo Hollowed plate for a heat exchanger with fluid flow tubes
JPS63159683U (en) * 1987-04-08 1988-10-19
FR2770632A1 (en) 1997-11-06 1999-05-07 Valeo Thermique Moteur Sa Heat exchanger with reinforced collector
US20070131404A1 (en) 2005-12-09 2007-06-14 Denso Corporation Heat exchanger
US20130160973A1 (en) * 2010-03-31 2013-06-27 Valeo Systemes Thermiques Heat exchanger having enhanced performance
US20140332190A1 (en) * 2011-12-19 2014-11-13 Valeo Systemes Thermiques Collector Box For A Heat Exchanger, In Particular For A Motor Vehicle, Cover For Said Box, And Heat Exchanger Including Such A Box

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4316503A (en) * 1979-10-12 1982-02-23 Nippondenso Co., Ltd. Solderless heat exchanger
US4360060A (en) * 1980-06-05 1982-11-23 Valeo Hollowed plate for a heat exchanger with fluid flow tubes
JPS63159683U (en) * 1987-04-08 1988-10-19
FR2770632A1 (en) 1997-11-06 1999-05-07 Valeo Thermique Moteur Sa Heat exchanger with reinforced collector
US20070131404A1 (en) 2005-12-09 2007-06-14 Denso Corporation Heat exchanger
US20130160973A1 (en) * 2010-03-31 2013-06-27 Valeo Systemes Thermiques Heat exchanger having enhanced performance
US20140332190A1 (en) * 2011-12-19 2014-11-13 Valeo Systemes Thermiques Collector Box For A Heat Exchanger, In Particular For A Motor Vehicle, Cover For Said Box, And Heat Exchanger Including Such A Box

Similar Documents

Publication Publication Date Title
US5450896A (en) Two-piece header
JP4171760B2 (en) Flat tube and manufacturing method of flat tube
US5209292A (en) Condenser header and tank assembly with interference fit baffle
EP1172623B1 (en) Heat exchanger and fluid pipe therefor
US20170198975A1 (en) Heat Exchanger Construction
US20130220585A1 (en) Tube for heat exchanger
US5749412A (en) Heat exchanger having a tubular header with a fastening lug
US20100025028A1 (en) Heat exchanger with receiver tank
US5513700A (en) Automotive evaporator manifold
JP2017531149A (en) Header plate, header box and heat exchanger for heat exchanger
US20070181291A1 (en) Heat exchanger and method of manufacturing the same
US11493283B2 (en) B-tube reform for improved thermal cycle performance
JPH09126685A (en) Heat exchanger
LU101721B1 (en) Heat exchanger
LU101675B1 (en) Heat exchanger with header plate reinforcement
JP2898800B2 (en) Heat exchanger
US7311138B2 (en) Stacking-type, multi-flow, heat exchangers and methods for manufacturing such heat exchangers
US20140190675A1 (en) Heat Exchanger Pipe And Heat Exchanger Incorporating Such Pipes
CN114341580A (en) Tank structure of heat exchanger
LU101492B1 (en) Flat heat exchanger tube
JP2020003089A (en) Heat exchange tube and heat exchanger
JP2003065694A (en) Heat exchanger
JP4541009B2 (en) Heat exchanger
US20080230214A1 (en) Heat exchanger and method of manufacturing the same
JP5525805B2 (en) Heat exchanger

Legal Events

Date Code Title Description
FG Patent granted

Effective date: 20210930

PD Change of ownership

Owner name: ESTRA AUTOMOTIVE SYSTEMS LUXEMBOURG S.A R.L.; LU

Free format text: FORMER OWNER: HT HOLDING LUXEMBOURG S.A.

Effective date: 20220317