U.S. patent application number 12/128406 was filed with the patent office on 2009-12-03 for heat exchanger.
This patent application is currently assigned to Steve Larouche. Invention is credited to Yves Bouchard, Steve Larouche.
Application Number | 20090294111 12/128406 |
Document ID | / |
Family ID | 41378340 |
Filed Date | 2009-12-03 |
United States Patent
Application |
20090294111 |
Kind Code |
A1 |
Larouche; Steve ; et
al. |
December 3, 2009 |
HEAT EXCHANGER
Abstract
A heat exchanger includes a core portion and at least one
substantially straight header plate. The core portion includes a
plurality of heat exchanger tubes and fins disposed alternatively.
The at least one substantially straight header plate has a
plurality of insertion slots extending therethrough for receiving a
respective end of the heat exchanger tubes therein, the core
portion and the at least one header plate being brazeable
together
Inventors: |
Larouche; Steve; (Jonquiere,
CA) ; Bouchard; Yves; (Jonquiere, CA) |
Correspondence
Address: |
SUTHERLAND ASBILL & BRENNAN LLP
999 PEACHTREE STREET, N.E.
ATLANTA
GA
30309
US
|
Assignee: |
Larouche; Steve
Saguenay
CA
|
Family ID: |
41378340 |
Appl. No.: |
12/128406 |
Filed: |
May 28, 2008 |
Current U.S.
Class: |
165/173 ;
29/890.03 |
Current CPC
Class: |
Y10T 29/4935 20150115;
F28D 1/05366 20130101; F28F 2265/26 20130101; F28F 9/001 20130101;
F28F 2275/04 20130101 |
Class at
Publication: |
165/173 ;
29/890.03 |
International
Class: |
F28F 9/02 20060101
F28F009/02; B21D 53/02 20060101 B21D053/02 |
Claims
1. A heat exchanger comprising: a core portion including a
plurality of heat exchanger tubes and fins disposed alternatively;
and at least one substantially straight header plate having a
plurality of insertion slots extending therethrough for receiving a
respective end of the heat exchanger tubes therein, the core
portion and the at least one header plate being brazeable
together.
2. A heat exchanger as claimed in claim 1, wherein the distance
between external edges of the at least one header plate and the
outermost heat exchanger tubes ranges between 1.3 and 3.2 mm.
3. A heat exchanger as claimed in claim 1, wherein the at least one
header plate has a thickness ranging between 2.0 and 12.7 mm.
4. A heat exchanger as claimed in claim 1, comprising at least one
tank cover weldable to the at least one header plate and defining a
tank cavity with the at least one header plate when secured
thereto, the heat exchanger tubes being in fluid communication with
the tank cavity.
5. A heat exchanger as claimed in claim 4, wherein the at least one
tank cover is welded to an outer surface of the at least one header
plate, proximate to external edges thereof.
6. A heat exchanger as claimed in claim 4, wherein the at least one
tank cover is welded to the brazed core portion and the at least
one header plate assembly.
7. A heat exchanger as claimed in claim 1, wherein at least one of
the heat exchanger tubes, the fins, and the at least one header
plate includes a clad for brazing the core portion and the at least
one header plate together.
8. A heat exchanger as claimed in claim 1, wherein the at least one
header plate comprises two header plates parallel to each other and
wherein the header plates are upwardly extending external edge
free.
9. A heat exchanger as claimed in claim 8, wherein the header
plates are substantially rectangular and have a length ranging
between 75 mm and 1020 mm and a width ranging between 12.7 mm and
180 mm.
10. A heat exchanger comprising: a core portion including a
plurality of heat exchanger tubes; at least one substantially
straight header plate having a plurality of insertion slots defined
therein for receiving a respective end of the heat exchanger tubes
therein, the core portion and the at least one header plate being
brazeable together; and at least one tank cover securable to the at
least one header plate and defining a tank cavity with the at least
one header plate when secured thereto, the heat exchanger tubes
being in fluid communication with the tank cavity.
11. A heat exchanger as claimed in claim 10, wherein the distance
between external edges of the at least one header plate and the
outermost heat exchanger tubes ranges between 1.3 and 3.2 mm.
12. A heat exchanger as claimed in claim 10, wherein the at least
one header plate has a thickness ranging between 2.0 and 12.7
mm.
13. A heat exchanger as claimed in claim 10, wherein the at least
one tank cover is weldable to an outer surface of the at least one
header plate, proximate to external edges thereof.
14. A heat exchanger as claimed in claim 10, wherein the at least
one tank cover is welded to the brazed core portion and the at
least one header plate assembly.
15. A heat exchanger as claimed in claim 10, wherein at least one
of the heat exchanger tubes and the at least one header plate
includes a clad for brazing the core portion and the at least one
header plate together.
16. A heat exchanger as claimed in claim 10, wherein the at least
one header plate comprises two header plates parallel to each other
and wherein the header plates are upwardly extending external edge
free,
17. A heat exchanger as claimed in claim 10, wherein the core
portion comprises fins in alternating succession with the heat
exchanger tubes.
18. A method for manufacturing a heat exchanger comprising:
inserting a respective end of a plurality of heat exchanger tubes
in a respective insertion slot extending through a substantially
straight header plate to define a heat exchanger tube and header
plate assembly; and brazing the heat exchanger tube and header
plate assembly.
19. A method as claimed in claim 18, further comprising securing a
tank cover to the straight header plate for defining a tank cavity,
the heat exchanger tubes being in fluid communication with the tank
cavity.
20. A method as claimed in claim 19, further comprising welding the
tank cover to an outer surface of the header plate, proximate to
external edges thereof.
21. A method as claimed in claim 19, wherein the securing step is
carried out after the brazing step.
22. A method as claimed in claim 18, further comprising disposing
corrugated fins between consecutive heat exchanger tubes and
wherein the brazing step is carried out on the heat exchanger tube
and straight header plate assembly including the corrugated
fins.
23. A method as claimed in claim 18, further comprising creating
the insertion slots in the header plate wherein the distance
between external edges of the header plate and the outermost
insertion slots ranges between 1.3 and 3.2 mm.
24. A heat exchanger header comprising: a brazeable substantially
straight header plate having an inner surface, an outer surface
opposed to the inner surface, a plurality of tube insertion slots
extending throughout the header plate and extending in a
longitudinal succession; and a tank cover having peripheral edges
secured to the outer surface of the header plate, proximate to
external edges of the header plate, and defining a tank cavity with
the header plate, the tube insertion slots being in fluid
communication with the tank cavity.
25. A heat exchanger header as claimed in claim 24, wherein the
distance between the external edges of the header plate and the
outermost insertion slots ranges between 1.3 and 3.2 mm.
26. A heat exchanger header as claimed in claim 24, wherein the
header plate has a thickness ranging between 2.0 and 12.7 mm.
27. A heat exchanger header as claimed in claim 24, wherein the
tank cover is welded to the header plate after the header plate has
been brazed.
28. A heat exchanger header as claimed in claim 24, wherein the
header plate includes a clad to braze the header plate with a core
portion.
29. A heat exchanger header as claimed in claim 24, wherein the
header plate is substantially rectangular and has a length ranging
between 75 mm and 1020 mm and a width ranging between 12.7 mm and
180 mm.
Description
FIELD OF THE INVENTION
[0001] The invention relates to heat exchangers and, more
particularly, to a method for manufacturing heat exchangers such as
radiators, oil coolers, air-to-air heat exchangers (charge air
coolers "CAC"), compressors, fuel coolers, conditioned air units,
and the like.
DESCRIPTION OF THE PRIOR ART
[0002] Radiators are heat exchangers that are used to reject heat
from the coolant of an internal combustion engine to the ambient.
The engine coolant is typically circulated through coolant passages
in the engine block to the so-called liquid side of the radiator
where it is cooled and then returned to the engine block. Cooling
occurs by forcing ambient air through the radiator core.
[0003] The thermal efficiency of an engine typically increases as
its operating temperature is increased. Consequently, it is
desirable to raise the operating temperature of the engine as much
as possible to maximize efficiency. The operating temperature can
hardly be raised to the point where the coolant within cooling
passages in the engine begins to vaporize.
[0004] Consequently, if engines are to be operated at higher
temperatures, it is necessary that the boiling point of the coolant
being employed be raised. This can be done by increasing system
pressure. At the same time, it becomes necessary to increase the
strength of the radiator I heat exchanger so that the same can
operate at the increased pressure.
[0005] Oil coolers are heat exchangers wherein heat dissipation
occurs through oil. Oil viscosity increases in cold temperature.
Thus, when operating in relatively cold conditions or when the
motor associated with the oil cooler is cold, the oil cooler must
sustain high pressure.
[0006] Finally, radiators and charge air coolers have a longer
operating life if they can support higher pressure when operating
in high vibrating environment.
BRIEF SUMMARY OF THE INVENTION
[0007] It is therefore an aim of the present invention to address
the above mentioned issues.
[0008] According to a general aspect, there is provided a heat
exchanger comprising: a core portion including a plurality of heat
exchanger tubes and fins disposed alternatively; and at least one
substantially straight header plate having a plurality of insertion
slots extending therethrough for receiving a respective end of the
heat exchanger tubes therein, the core portion and the at least one
header plate being brazeable together.
[0009] According to another general aspect, there is provided a
heat exchanger comprising: a core portion including a plurality of
heat exchanger tubes; at least one substantially straight header
plate having a plurality of insertion slots defined therein for
receiving a respective end of the heat exchanger tubes therein, the
core portion and the at least one header plate being brazeable
together; and at least one tank cover securable to the at least one
header plate and defining a tank cavity with the at least one
header plate when secured thereto, the heat exchanger tubes being
in fluid communication with the tank cavity.
[0010] According to still another general aspect, there is provided
a method for manufacturing a heat exchanger comprising: inserting a
respective end of a plurality of heat exchanger tubes in a
respective insertion slot extending through a substantially
straight header plate to define a heat exchanger tube and header
plate assembly; and brazing the heat exchanger tube and header
plate assembly.
[0011] According to a further general aspect, there is provided a
heat exchanger header comprising: a brazeable substantially
straight header plate having an inner surface, an outer surface
opposed to the inner surface, a plurality of tube insertion slots
extending throughout the header plate and extending in a
longitudinal succession; and a tank cover having peripheral edges
secured to the outer surface of the header plate, proximate to
external edges of the header plate, and defining a tank cavity with
the header plate, the tube insertion slots being in fluid
communication with the tank cavity.
BRIEF DESCRIPTION OF THE DRAWINGS
[0012] FIG. 1 is a perspective view of a heat exchanger in
accordance with an embodiment;
[0013] FIG. 2 is a sectional view taken along cross-section lines
2-2 of FIG. 1 of the heat exchanger;
[0014] FIG. 3 is a perspective view of a core portion and two
header plates of the heat exchanger shown in FIG. 1;
[0015] FIG. 4 includes FIG. 4a and FIG. 4b, FIG. 4a is a top plan
view of the core portion and one of the header plates shown in FIG.
3 and FIG. 4b is an enlarged view, fragmented, of heat exchanger
tubes inserted in cavities defined in one of the header plates;
[0016] FIG. 5 is a perspective view, partly sectioned and
fragmented, of the heat exchanger shown in FIG. 1; and
[0017] FIG. 6 is a flow chart illustrating a method for
manufacturing the heat exchanger shown in FIG. 1.
[0018] It will be noted that throughout the appended drawings, like
features are identified by like reference numerals.
DETAILED DESCRIPTION
[0019] FIGS. 1 and 2 show a heat exchanger 10 having a housing 12
covering a core portion 14 and extending between a pair of hollow
headers 16 disposed in parallel with each other. Fluid inlet and
outlet connectors 18 are mounted to the headers 16 and are in fluid
communication with a tank cavity 20 defined in the hollow headers
16, as will be described in more details below.
[0020] The housing 12 includes two opposed and spaced-apart side
plates 24 having an edge secured to headers 16.
[0021] FIGS. 2 and 3 show an internal view of the heat exchanger
10. The core portion 14 includes a plurality of heat exchanger flat
tubes 26 disposed in parallel with their opposite sides in fluid
communication with the hollow headers 16. Corrugated fins 28 are
disposed between adjacent heat exchanger tubes 26 and outside the
outermost heat exchanger tubes 26. The side plates 24, defining a
portion of the housing 12, are disposed outside the outermost
corrugated fins 28.
[0022] The heat exchanger tubes 26 are hollow extruded articles
defining an inner channel 30 with an obround cross-section. The
inner channel 30 is in fluid communication with the tank cavities
20. The inner channel 30 can be divided into a plurality of
passages with partition walls (not shown), also called
micro-channel tubes, extending longitudinally therein to reinforce
the tubes 26.
[0023] Each header 16 includes a substantially straight rectangular
header plate 32 having an inner surface 34 and an opposed outer
surface 36. The substantially straight header plates 32 do not
include upwardly extending peripheral edges like in prior art heat
exchangers. The inner surfaces 34 of both headers 16 face one
another when the heat exchanger 10 is assembled. A plurality of
tube insertion slots 38 extend throughout the header plates 32 in a
longitudinal succession as shown in FIG. 4a. The insertion slots 38
are defined to receive therein an end of one heat exchanger tube
26. FIG. 4b shows that the outer surface of the heat exchanger
tubes 26, proximate to an end thereof, is juxtaposed to the inner
surface of the insertion slots 38. Thus, the external size of the
heat exchanger tubes 26 is slightly smaller than the size of the
insertion slots 38. In an embodiment, the insertion slots 38 in
header plate 32 are created by machining.
[0024] FIGS. 2 and 5 show that each header 16 also includes a tank
cover 40 having an upper wall 42, two opposed and spaced-apart
lateral walls 44, and two opposed and spaced-apart side walls 46,
extending between the lateral walls 44. The lateral walls 44 and
the side walls 46 have peripheral edges 48 secured to the outer
surface 36 of the header plate 32, proximate to external edges 50
of the header plate 32. For example and without being limitative,
the peripheral edges 48 of the tank cover 40 can be welded to the
header plate 32. In the embodiment shown, the side walls 46 are
recessed internally from the external edges 50 of the header plate
32. The tank cover 40 and the header plate 32 define the tank
cavity 20 when secured together.
[0025] In an alternative embodiment (not shown), the peripheral
edges 48 of the tank cover 40 can be welded to the lateral walls of
the heater plate 32, i.e. the walls extending between the inner
surface 34 and the outer surface 36. In another alternative
embodiment (not shown), the outer surface 36 of the heater plate 32
can include a peripheral recess section in which the peripheral
edges 48 of the tank cover 40 are inserted and secured. The
peripheral recess section can be machined in the header plate 32.
In another alternative embodiment (not shown), both the edges of
the header plate 32 and the peripheral edges 48 of the tank cover
40 can be beveled edges which are matingly engaged when securing
the tank cover 40 to the header plate 32.
[0026] The tank cavity 20 is in fluid communication with the inner
channels 30 of the heat exchanger tubes 26 inserted in the tube
insertion slots 38 and with the fluid inlet and outlet connectors
18.
[0027] In the embodiment described above, the heat exchanger is a
single tube pass heat exchanger wherein the fluid enters the heat
exchanger at one end, flows once in the tubes, and exits at the
opposed heat exchanger end. In alternative embodiments, the heat
exchanger can be a multiple tube pass heat exchanger such as and
without being limitative a double tube pass or a triple tube pass
heat exchanger. For example and without being limitative, in a
double tube pass heat exchanger, the fluid enters the heat
exchanger at a first end, flows twice in the tubes, and exits at
the first end. Similarly, in a triple tube pass heat exchanger, the
fluid enters the heat exchanger at a first end, flows thrice in the
tubes, and exits at the opposed heat exchanger end. In multiple
tube pass heat exchangers, at least one of the tank covers includes
a partition wall which separated the tank cavity into separated
chambers. It is appreciated that the heat exchanger can include
more than three passes.
[0028] Referring now to FIG. 6, for manufacturing a heat exchanger,
the core portion is first assembled to the header plates 70. The
heat exchanger tubes and the corrugated fins are stacked
alternatively and the opposite ends of the heat exchanger tubes are
inserted in the corresponding insertion slots defined in the header
plates to form a provisional assembly, as shown in FIG. 3. The
edges of the heat exchanger tubes extend substantially flush with
the outer face of the header plate in which they are inserted.
Furthermore, side plates are assembled to the core portion. Then,
this provisional assembly is integrally brazed in a furnace 72.
[0029] The brazing step is carried out in a controlled environment
in an atmosphere of inert gas such as nitrogen, for instance,
during 10 to 20 minutes and, in an alternative embodiment, during
12 to 18 minutes. The temperature in the furnace ranges between
approximately 1000 and 1200.degree. F. (approximately 530 and
650.degree. C.). It is appreciated that the brazing conditions
(temperature, atmosphere, time, etc.) can vary in accordance with
the heat exchanger size and materials.
[0030] More particularly, in an embodiment, prior to the brazing
step, a brazing flux is deposited on the provisional assembly
through electromagnetism. The use of these fluxing agents with
aluminum heat exchangers promotes the dissociation and disruption
of the native aluminum oxide (Al.sub.2O.sub.3). Then, the
provisional assembly is introduced in a controlled environment
where vacuum is created. Nitrogen is introduced and the temperature
in the controlled environment is increased to approximately
400-450.degree. F. (approximately 200 and 230.degree. C.) for a
pre-heating step. Following the pre-heating step, the provisional
assembly is brazed as mentioned above. The brazed assembly is then
cooled in the controlled environment, under nitrogen, wherein the
temperature is lowered to approximately 400.degree. F. Finally, the
brazed assembly is removed from the controlled environment and
cooled to ambient temperature under forced air convection.
[0031] Then, the tank covers are mounted to a respective header
plate and secured thereto 74. In an embodiment, the peripheral
edges of the tank covers are secured to the outer face of the
header plate, proximate to external edges of the header plate, to
define the tank cavity. The peripheral edges can be welded to the
header plate for securing the tank covers.
[0032] Finally, the side plates are sawed to create dilatation
joints 54 (FIG. 1) therein 76. It is appreciated that, in an
alternative embodiment, the dilatation joints can be sawed before
securing the tank cover to the brazed assembly.
[0033] In an alternative embodiment, the provisional assembly can
include tank covers. The tank covers are thus secured by brazing
simultaneously with the other components. They can also be welded
to the header plates prior to the brazing step.
[0034] The heat exchanger tubes, the corrugated fins, and the
headers 16 are made of an aluminum alloy adapted for heat exchanger
applications. For example and without being limitative, they can be
made of AA 3003. The heat exchanger tubes, the corrugated fins, and
the header plates include a surface clad. For example and without
being limitative, the clad material can be 4000 series aluminum. It
is appreciated that, in alternative embodiments, other aluminum
alloys adapted for heat exchanger and brazing applications can be
used.
[0035] The header plates can either have a clad on both sides or on
only one side, either the inner surface or the outer surface.
Similarly, the corrugated fins can have a clad on both sides or on
only one side. The outer surface of the heat exchanger tubes
includes the clad material. The clad material can represent between
2 and 15% of the heat exchanger component thickness. In an
alternative embodiment, the clad material can represent between 5
and 10% of the heat exchanger component thickness.
[0036] In a non-limitative embodiment, the header plates are
rectangular with a length ranging between 75 and 1020 millimeters
(mm) (2.95 and 40.0 inches), a width ranging between 12.7 and 180
mm (0.5 and 7.0 inches), and a thickness ranging between 2.0 and
12.7 mm (0.08 and 0.5 inch). In an alternative embodiment, the
header plates have a length ranging between 100 and 950 mm (4 and
37.5 inches), a width ranging between 19 and 170 mm (0.75 and 6.75
inches), and a thickness ranging between 2.5 and 10 mm (0.1 and 0.4
inch).
[0037] In an embodiment, the heat exchanger tubes have a cross
section length (major diameter) ranging between 19 and 120 mm (0.75
and 4.8 inches) and a cross-section width (minor diameter) ranging
between 2 and 12 mm (0.08 and 0.5 inch). In an alternative
embodiment, the heat exchanger tubes have a cross section length
ranging between 25 and 80 mm (1.0 and 3.15 inches) and a
cross-section width ranging between 3.7 and 7 mm (0.15 and 0.28
inch).
[0038] In an embodiment, the thickness of the heat exchanger tube
wall ranges between 0.1 and 3.6 mm (0.004 and 0.14 inch) and in an
alternative embodiment, the thickness of the heat exchanger wall
ranges between 0.2 and 3.2 mm (0.008 and 0.125 inch). In an
embodiment, the thickness of the heat exchanger tube wall can vary
along the tube length.
[0039] In an embodiment, the distance between the external edges of
the header plate and the outermost heat exchanger tubes ranges
between 1.3 and 3.2 mm (0.05 and 0.125 inch). In an alternative
embodiment, this distance ranges between 1.3 and 6.4 mm (0.05 and
0.25 inch).
[0040] As mentioned above, the thickness of the header plates
ranges between 2.0 and 12.7 mm (0.08 and 0.50 inch). In comparison
with the headers of prior art heat exchangers, the header plate is
thicker, providing an increased stiffness to the resulting heat
exchanger and a stronger physical bond between the heat exchanger
tubes and the header plate since brazing occurs on a larger surface
area. The resulting header plate and tube exchanger assembly can
thus support higher pressure.
[0041] Moreover, the outermost heat exchanger tubes are mounted
proximate to the external edge of the header plate since the header
plate is substantially straight. Thus, the moment arm between the
junction of the exchanger tubes and the header plate and the
external edges of the header plate is reduced. The resulting heat
exchangers have improved mechanical properties, such as higher
pressure resistance, stiffness, vibration resistance, and impact
strength, comparatively to prior art heat exchangers.
[0042] Comparatively, to prior art heat exchangers wherein the tank
cover is mounted inwardly of the header plates having turn up
edges, the heat exchanger has a higher burst pressure strength. For
example, in an embodiment, the heat exchanger withstood 1825 psi
comparatively to 580 psi for the prior art heat exchanger.
Moreover, the heat exchanger did not show any cracking
comparatively to the prior art heat exchanger which showed cracking
at 300 psi.
[0043] It is appreciated that the heat exchangers described above
can be used in radiators, compressors, fuel coolers, conditioned
air units, air-to-air heat exchangers (charge air coolers), oil
coolers, and the like.
[0044] It can be used in new products (OEM) or replacement
products.
[0045] The embodiments of the invention described above are
intended to be exemplary only. For example, the shape of the heat
exchanger tubes can vary and the shape of the insertion slots can
vary accordingly. Furthermore and without being limitative, the
shape of the headers can vary. The position of fluid inlet and
outlet connectors can be modified from the one described above in
reference to FIG. 1, which is typically associated with oil
coolers. For example and without being limitative, for radiators
and charge air coolers, the fluid inlet and outlet connectors can
be centrally mounted to a respective hollow header.
[0046] The scope of the invention is therefore intended to be
limited solely by the scope of the appended claims.
* * * * *