U.S. patent application number 13/873022 was filed with the patent office on 2014-10-30 for heat exchanger.
This patent application is currently assigned to Ford Global Technologies, LLC. The applicant listed for this patent is FORD GLOBAL TECHNOLOGIES, LLC. Invention is credited to Christopher Mark Greiner, Lawrence M. Rose.
Application Number | 20140318753 13/873022 |
Document ID | / |
Family ID | 51685203 |
Filed Date | 2014-10-30 |
United States Patent
Application |
20140318753 |
Kind Code |
A1 |
Greiner; Christopher Mark ;
et al. |
October 30, 2014 |
HEAT EXCHANGER
Abstract
A heat exchanger is provided. The heat exchanger includes a
plurality of stacked layers of fins, each fin including a repeated
pattern of folds, the plurality of stacked layers of fins forming a
plurality of repeating offset cell structures and a first coolant
duct and a second coolant duct coupled to peripheral fins in the
plurality of stacked layers of fins. The heat exchanger further
includes a fan directing air through the repeating offset cell
structures.
Inventors: |
Greiner; Christopher Mark;
(Birmingham, MI) ; Rose; Lawrence M.; (Berkley,
MI) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
FORD GLOBAL TECHNOLOGIES, LLC |
Dearborn |
MI |
US |
|
|
Assignee: |
Ford Global Technologies,
LLC
Dearborn
MI
|
Family ID: |
51685203 |
Appl. No.: |
13/873022 |
Filed: |
April 29, 2013 |
Current U.S.
Class: |
165/166 |
Current CPC
Class: |
F28F 13/12 20130101;
F28D 2021/0094 20130101; F28F 1/126 20130101; F28F 3/08 20130101;
F28D 1/05366 20130101 |
Class at
Publication: |
165/166 |
International
Class: |
F28F 3/08 20060101
F28F003/08 |
Claims
1. A heat exchanger comprising: a plurality of stacked layers of
fins, each fin including a repeated pattern of folds, the plurality
of stacked layers of fins forming a plurality of repeating offset
cell structures; a first coolant duct and a second coolant duct
coupled to peripheral fins in the plurality of stacked layers of
fins; and a fan directing air through the repeating offset cell
structures.
2. The heat exchanger of claim 1, where the airflow through the
repeating offset cell structures is isotropically turbulent.
3. The heat exchanger of claim 1, where the plurality of stacked
layers include a first stacked layer having a plurality of fins
sequentially stacked and aligned in a transverse direction
extending between the first and second coolant duct and a second
stacked layer having a plurality of fins sequentially stacked and
aligned in the transverse direction, the first stacked layer is
offset from the second stacked layer in longitudinal direction.
4. The heat exchanger of claim 3, where the longitudinal direction
extends between the inlets and the outlets of the first and second
coolant ducts.
5. The heat exchanger of claim 1, where each of the fins are
identical in size and geometry.
6. The heat exchanger of claim 1, where each of the fins extend in
a longitudinal direction from inlets of the first and second
coolant ducts to outlets of the first and second coolant ducts.
7. The heat exchanger of claim 1, where the stacked layer of fins
are angled at 15.degree. with regard to the general direction of
airflow generated by the fan.
8. The heat exchanger of claim 1, where each of the fins are formed
of a continuous piece of material.
9. The heat exchanger of claim 1, where the cell structures have a
square cross-section.
10. The heat exchanger of claim 1, where each of the fins includes
a plurality of consecutively arranged planar surfaces.
11. The heat exchanger of claim 1, where each of the fins includes
a plurality of square air-flow channels and where each air-flow
channel is bounded by three consecutively arranged planar
sides.
12. The heat exchanger of claim 1, where each of the fins includes
a plurality of triangular air-flow channels and where each air-flow
channel is bounded by two consecutively arranged planar sides.
13. A method for heat exchanger operation, comprising: flowing
coolant through a first coolant duct and a second coolant duct; and
flowing turbulent air through a plurality of repeating offset cell
structures formed by a plurality of stacked layers of fins, each
fin including a repeated pattern of folds.
14. The method of claim 13, where the airflow through the plurality
of repeating offset cell structures is isotropically turbulent.
15. The method of claim 13, where the offset cell structures are
arranged at a non-straight angle with regard to an outlet direction
of a fan.
16. A heat exchanger for an engine, comprising: a first and second
coolant ducts spaced way from one another; a first layer of stacked
and transversely aligned fins extending between the first and
second coolant ducts, each of the fins included a repeating pattern
of folds; and a second layer of stacked and transversely aligned
fins extending between the first and second coolant ducts, each of
the fins included a repeating pattern of folds and the first layer
of fins longitudinally offset from the second layer of fins.
17. The heat exchanger of claim 16, where a plurality of planar
surfaces in peripheral fins in the first and second layer are in
face sharing contact with a surface of either the first coolant
duct or the second coolant duct.
18. The heat exchanger of claim 16, where the fins in the first
layer and the second layer form a plurality of offset cell
structures.
19. The heat exchanger of claim 16, where a range of ratios between
a width and a length of each of the repeating planar surfaces is
1/1-1/15.
20. The heat exchanger of claim 16, where each of the fin
structures includes a plurality of consecutively arranged planar
surfaces, each planar surface arranged perpendicular to the
subsequent and preceding planar surfaces.
Description
FIELD
[0001] The present disclosure relates to a heat exchanger and
method for operation of a heat exchanger.
BACKGROUND AND SUMMARY
[0002] Heat exchanger designs, such as automotive heat exchangers,
may utilize rolled and/or folded fins to transfer heat to the air
from a coolant or fluid that passes internally through a series of
coolant tubes. Heat is conducted from the tubes to the fins where
the fins physically contact the coolant tubes. U.S. 2012/0273182
discloses a heat exchanger having a fin member repeatedly extending
between pipes in a corrugated folding pattern. The fin member
removes heat from the pipes and discharges it into the air flowing
through the fin.
[0003] The inventors have recognized several drawbacks with the
heat exchanger disclosed in U.S. 2012/0273182. For instance, due to
the uniformity of the fin design a small amount of turbulence may
be generated in the air flowing through the fins. Decreasing
turbulence decreases the heat transfer capability of the heat
exchanger. Additionally, the small contacted area between the fins
and the pipes further decreases the heat transfer capability of the
heat exchanger. Consequently, the size of the heat exchanger may be
increased to provide a desired amount of cooling.
[0004] The inventors herein have recognized the above issues and
developed a heat exchanger. The heat exchanger includes a plurality
of stacked layers of fins, each fin including a repeated pattern of
folds, the plurality of stacked layers of fins forming a plurality
of repeating offset cell structures. The heat exchanger further
includes a first coolant duct and a second coolant duct coupled to
peripheral fins in the plurality of stacked layers of fins. The
heat exchanger further includes a fan directing air through the
repeating offset cell structures.
[0005] The flow pattern generated by the offset cell structures
increases turbulence in the airflow through the stacked layers of
fins without increasing airflow losses through the cell structure
beyond a desirable value. As a result, the heat transfer capability
of the heat exchanger is increased. Specifically, in one example
the repeating offset cell structures are configured to generate
isotropically turbulent airflow through the fins. It will be
appreciated that isotropically turbulent airflow further increases
the amount of heat transferred to the air from the fins.
Additionally, when the heat transfer capacity of a heat exchanger
is increased the size of the heat exchanger may be decreased while
achieving a heat transfer capacity of a larger less efficient heat
exchanger. As a result, the compactness of the cooling system may
be increased or the heat exchanger may provide increased
cooling.
[0006] Additionally in one example, a plurality of planar surfaces
of the peripheral fins may be coupled to the first and second
coolant ducts. In this way, the size of the contact regions between
the fins and the coolant ducts is increased, further increasing the
heat transfer capability of the heat exchanger.
[0007] The above advantages and other advantages, and features of
the present description will be readily apparent from the following
Detailed Description when taken alone or in connection with the
accompanying drawings.
[0008] It should be understood that the summary above is provided
to introduce in simplified form a selection of concepts that are
further described in the detailed description. It is not meant to
identify key or essential features of the claimed subject matter,
the scope of which is defined uniquely by the claims that follow
the detailed description. Furthermore, the claimed subject matter
is not limited to implementations that solve any disadvantages
noted above or in any part of this disclosure. Additionally, the
above issues have been recognized by the inventors herein, and are
not admitted to be known.
BRIEF DESCRIPTION OF THE DRAWINGS
[0009] FIG. 1 shows a schematic depiction of a vehicle system
including an engine and a heat exchanger;
[0010] FIG. 2 shows an example heat exchanger;
[0011] FIG. 3 shows a portion of a fin structure in the heat
exchanger shown in FIG. 2;
[0012] FIG. 4 shows a fin in the fin structure shown in FIG. 3;
[0013] FIG. 5 shows another example heat exchanger;
[0014] FIG. 6 shows the heat exchanger illustrated in FIG. 5
without one of the coolant ducts;
[0015] FIG. 7 shows a portion of a fin structure in the heat
exchanger shown in FIGS. 5 and 6;
[0016] FIG. 8 shows a fin in the fin structure shown in FIG. 7;
[0017] FIG. 9 shows another heat exchanger;
[0018] FIG. 10 shows the heat exchanger illustration in FIG. 9
without one of the coolant ducts;
[0019] FIG. 11 shows a detailed view of a portion of the fin
structure shown in FIGS. 9 and 10;
[0020] FIG. 12 shows a view of layers of fins included in the fin
structure shown in FIG. 3;
[0021] FIG. 13 shows an example pyramid type structure; and
[0022] FIG. 14 shows a method for operation of a heat
exchanger.
DETAILED DESCRIPTION
[0023] A heat exchanger having a plurality of stacked layers of
fins forming a plurality of repeating offset cell structures is
described herein. Peripheral fins in the plurality of stacked
layers of fins are coupled to a first and second coolant duct. The
offset cellular fin design offers a number of performance
enhancements over previous designs such as increasing heat transfer
from the fins to the air via increased turbulence (e.g., isotropic
turbulence) generation and increased fin surface area.
Specifically, the offset cells generate a desired amount of airflow
turbulence within the heat exchanger without increasing the
pressure drop in airflow across the heat exchanger above a
desirable level. In this way, the heat rejection capacity of the
heat exchanger is increased. Moreover, the offset cellular fin
design is also less susceptible flow disruption caused by fin
deformation (e.g., crushing), cell obstruction, and other types of
degradation of the fins due to the large number of interconnected
flow paths in the cell structures, providing alternate flow paths
around the damaged/obstructed regions.
[0024] Additionally, in some examples planar surfaces in the
peripheral fins may be in face sharing contact with surfaces of the
coolant ducts. Consequently, heat conduction from the coolant ducts
(e.g., coolant tubes) to the fins is increased due to an increase
of contact area between the tube and fins when compared to fins
coupled to the tube via edges of the fins. The aforementioned
benefits enable an increase in the heat rejection capacity of the
heat exchanger. Consequently, the size and weight of the heat
exchanger may be reduced or the heat rejection capacity of the heat
exchanger may be increased.
[0025] FIG. 1 shows a schematic depiction of a vehicle system 10
including an engine 12 and a heat exchanger 50. The engine 12 is
configured to implement combustion operation. For example, a four
stroke combustion cycle may be implemented including an intake
stroke, a compression stroke, a power stroke, and an exhaust
stroke. However, other types of combustion cycles may be utilized
in other examples. It will be appreciated that heat is generated
during combustion. Therefore, the heat exchanger 50 is configured
to remove heat from the engine 12.
[0026] An intake sub-system 14 is included in the vehicle system 10
and configured to provide intake air to cylinders 16 in the engine
12, denoted via arrow 15. The vehicle system 10 further includes an
exhaust sub-system 18 configured to receive exhaust gas from
cylinders 16 in the engine 12, denoted via arrow 19. The engine 12
may be formed of a cylinder head 20 and a cylinder block 22.
[0027] One or more cooling passages 24 may traverse the cylinder
head 20 and/or cylinder block 22. The cooling passages 24 are in
fluidic communication with the heat exchanger 50, discussed in
greater detail herein. However, in other examples the heat
exchanger 50 maybe coupled to other suitable cooling systems in the
vehicle such as a turbocharger cooling system.
[0028] A fan 30 is also included in the vehicle system 10. The fan
30 is configured to direct air to the heat exchanger 50, depicted
via arrows 31. In this way, airflow may be generated by the fan to
increase the cooling via the heat exchanger. However, in other
examples the heat exchanger may be positioned at a location where
airflow is generated from vehicle motion. A pump 32 is also
included in the vehicle system 10. The pump 32 is coupled to the
coolant passages 24 and configured to circulate coolant through the
coolant passages 24.
[0029] The heat exchanger 50 is shown included in a vehicle cooling
system in FIG. 1. However, it will be appreciated that the heat
exchanger may be used in a variety of applications such as
residential air conditioners, industrial systems, etc.
[0030] FIGS. 2-4 show a first example heat exchanger 200. The heat
exchanger200 may be included in the vehicle system 10 shown in FIG.
1. Therefore, the heat exchanger 200, shown in FIGS. 2-4, may be
the heat exchanger 50 schematically depicted in FIG. 1.
[0031] FIG. 2 shows a perspective view of the first example heat
exchanger 200. The heat exchanger 200 includes a first coolant duct
202 spaced away from a second coolant duct 204. The first coolant
duct 202 and the second coolant duct 204 each include a coolant
inlet 206. Additionally, the first coolant duct 202 and the second
coolant duct 204 each include a coolant outlet 208. The coolant
inlets and outlets (206 and 208) may be in fluidic communication
with cooling passages 24 shown in FIG. 1 or with other suitable
coolant conduits, such as coolant conduits in a turbocharger
system, coolant conduits in an exhaust gas recirculation (EGR)
system, etc. Thus, a suitable coolant may flow through each of the
first and second coolant ducts (202 and 204). The coolant inlets
are positioned on the same side of the heat exchanger in the
depicted example. However, in other examples, the coolants inlets
may be positioned on opposing sides of the heat exchanger.
[0032] Continuing with FIG. 2, a fin structure 210 extending
between the first coolant duct 202 and the second coolant duct 204
is also included in the heat exchanger 50. The fin structure 210
includes a plurality of fins 212. Peripheral fins in the fin
structure 210 may be coupled to the first coolant duct 202 and the
second coolant duct 204. Each of the fins may extend from the
inlets 206 to the outlets 208 of the coolant ducts.
[0033] The direction extending from the inlets to the outlets is
referred to as a longitudinal direction. The direction
perpendicular to the longitudinal direction and extending between
the first coolant duct 202 and the second coolant duct 204 is
referred to as a transverse direction. A lateral direction,
perpendicular to the longitudinal direction, extending from a first
side of the coolant ducts to a second side of the coolant ducts is
referred to as a lateral direction. A longitudinal axis, transverse
axis, and a lateral axis are provided for reference.
[0034] It will be appreciated that the fan 30, shown in FIG. 1 may
be configured to direct air through the fin structure 210. The
airflow enables heat to be transferred from the heat exchanger to
the surrounding air. The general direction of airflow from the fan
may be perpendicular to the leading edge of the fin structure
210.
[0035] FIG. 3 shows an expanded view of a portion 300 of the fin
structure 210 shown in FIG. 2. As previously discussed, the fin
structure includes a plurality of fins 212. Additionally, each of
the fins 212 is equivalent in size and shape to the other fins in
the fin structure. However, a fin structure with fins having an
unequal size and/or shape has been contemplated.
[0036] The fin structure forms a plurality of repeating offset cell
structures 302. Offsetting the cell structures generates turbulence
(e.g., isotropic turbulence) in the air flowing through the fin
structure. Specifically, the fins of the cell structures may act as
a flat plate airfoil, causing the entering flow to split on both
sides of each of the fins. The splitting of the flow results in
turbulence generation, which is enhanced as the flow progresses
through the next layer of cells. Changing the relative direction of
the incoming flow to the cell axis can further enhance turbulent
generation as the flow will separate off the upper surface of each
flat plate airfoil fin.
[0037] As previously discussed, the airflow may be generated via a
fan and directed into the cell structures 302. It will be
appreciated that the general direction of airflow at the leading
edge of the fin structure is in a lateral direction. After the air
travels past the leading edge of the fin structure, turbulent
airflow may be generated. As shown, the cell structures 302 have a
square cross-section, the cutting plane of the cross-section
extending in a longitudinal and transverse direction. Again a
longitudinal axis, a transverse axis, and a lateral axis are
provided for reference. The cells may be divided into laterally
aligned sets. Therefore, each of the cells in a set has a similar
lateral position. Additionally, the sets of aligned cell structures
are offset in a longitudinal and transverse direction. The cell
structures 302 have square cross-sections. The cutting plane of the
cross-sections is perpendicular to a lateral axis. However, cell
structures having cross-sections with different geometries have
been contemplated. For example, the cell structures may have a
rectangular or triangular cross-section, in other examples.
Furthermore, due to the offset between the cells structures cells
in non-peripheral sections of the structure each flows air to four
downstream cell structures and/or receives air from four upstream
cell structures. In this way, a large number of flow paths are
formed in the fin structure, thereby increasing turbulence in the
fin structure as well as making it less susceptible to large drops
in airflow through the cell structures caused by damaged fins
and/or blocked cells.
[0038] The plurality of fins 212 may be divided into layers. The
fins in each of the layers are sequentially stacked and aligned in
a transverse direction and longitudinal direction. However, layers
having other orientations have been contemplated. Specifically, a
first layer of fins 310 and a second layer of fins 312 are shown in
FIG. 3. The first and second layers of fins are offset in a
longitudinal and transverse direction. It will be appreciated that
each of the layers of the fins shown in FIG. 3 may include
additional fins. Furthermore, each of the first layers of fins 310
and second layers of fins 312 extend between the first and the
second coolant ducts (202 and 204), shown in FIG. 2. In this way,
heat may be conducted from the coolant ducts to the fin
structure.
[0039] Each of the fins in the first layer of fins 310 are aligned
in a transverse direction. This alignment enables the cells (e.g.,
square cells) to be formed via the fin structure. Therefore, each
of the layers form a plurality of cells. It will be appreciated
that the first layer of fins 310 is offset from the second layer of
fins 312.
[0040] Peripheral fins 304 are shown in FIG. 3. The corners 306 in
the peripheral fins 304 may be coupled (e.g., braised) to a surface
(e.g., peripheral surface) of the first coolant duct 202, shown in
FIG. 2. Likewise, additional peripheral fins spaced away from the
peripheral fins 304 may be coupled to a surface (e.g., peripheral
surface) of the second coolant duct 204, shown in FIG. 2. The fins
may be coupled to adjacent fins via braising and/or other suitable
coupling techniques. For example, a portion of the fin structure
may be cast, extruded, etc.
[0041] Additionally, each fin in the fin structure further includes
laterally-peripheral edges. The laterally-peripheral edges 320 of
fins in the first layer of fins 310 are in contact with
laterally-peripheral edges 322 of fins in the second layer of fins
312. The edges (320 and 322) form perpendicular angles with one
another. However, other angles have been contemplated. In this way,
a large number of flow paths within the fin structure are created.
As a result, increased turbulence (e.g., isotropic turbulence) may
be generated in the air flowing through the fin structure during
operation of the heat exchanger.
[0042] Additionally, when the sequential layers of fins are
consecutively numbered, even numbered layers are transversely and
longitudinally aligned. Likewise, odd numbered layers are
transversely and longitudinally aligned and the even numbered
layers are offset (e.g., longitudinally and transversely offset)
from the odd numbered layers.
[0043] FIG. 12 shows another view of the first layer of fins 310
and the second layer of fins 312, shown in FIG. 3. The second layer
of fins 312 is dashed to highlight the distinction between the
layers. As shown, the first layer of fins 310 is offset by half the
lateral width 350 of one of the cells included in the layer of fins
from the second layer of fins 312. However, other degrees of offset
have been contemplated. For example, the first layer of fins may be
offset by a quarter of the lateral width of the cells from the
second layer of fins.
[0044] FIG. 4 shows one of the fins 400 included in the fin
structure 210 shown in FIGS. 2 and 3. As shown, the fin 400,
depicted in FIG. 4, includes a plurality of consecutively arranged
planar surfaces 402. All of the planar surfaces are equivalent in
size and shape. However, in other example some of the planar
surfaces may not be equivalent in size and/or shape.
[0045] An angle 402 is formed between consecutively arranged planar
surfaces. The angle 402 is 90 degrees, in the depicted example.
Therefore, the consecutively arranged planar surfaces are
perpendicular to one another. However, other angles between
consecutively arranged planar surfaces have been contemplated.
Thus, the fin 400 includes a repeating pattern of folds.
[0046] The fin 400 may be formed from a continuous piece of
material. Therefore, the fin 400 may be manufactured via extrusion,
casting, etc. The fin 400 may be constructed out of a suitable
material such as a metal (e.g., aluminum, steel, etc.). The width
452 of the fins may range from 2-3 mm. Further in another example
the width 452 of the fins may be .ltoreq.10 mm. The widths of the
fins may be selected based on the viscosity of the external cooling
fluid (e.g., air or liquids). Further in some examples, a ratio
between the width 452 and a length 454 of one of the planar
surfaces may be between 1/1-1/10 or 1/15.
[0047] As shown the fin 400 defines a plurality of triangular
air-flow channels 410. Each of the triangular air-flow channels 410
bounded by two consecutively arranged planar sides in the fin 400.
It will be appreciated that when fin 400 is coupled to adjacent
fins in a set of stacked fins, adjacent triangular air-flow
channels form square air-flow channels.
[0048] FIGS. 5-8 show another example of a heat exchanger 500 that
may be included in the vehicle system shown in FIG. 1. Thus, the
heat exchanger 500 may be the heat exchanger 50, shown in FIG. 1,
in some examples. Therefore, the heat exchanger 500 may receive a
suitable coolant from the coolant passages 24 shown in FIG. 1 or
coolant from another suitable system. Specifically, FIG. 5 shows a
first coolant duct 502 spaced away from a second coolant duct 504.
Both the first coolant duct and the second coolant duct include an
inlet 506 and an outlet 508. The heat exchanger 500 also includes a
fin structure 510 extending between the first and second coolant
ducts (502 and 504). The fin structure 510 includes a plurality of
fins 512. The fin structure 510 also extends between the inlets 506
and the outlets 508. However in other examples, the fin structure
510 may only partially extend between the inlets 506 and the
outlets 508. A longitudinal axis, lateral axis, and transverse axis
are provided for reference.
[0049] FIG. 6 shows the heat exchanger 500, shown in FIG. 5 without
the first coolant duct 502. Peripheral fins 600 included in the fin
structure 510 are shown in FIG. 6. It will be appreciated that
planar surfaces 602 of the peripheral fins 600 may be coupled to a
surface (e.g., peripheral surface) of the first coolant duct 502,
shown in FIG. 5. Specifically, the planar surfaces 602 may be in
face sharing contact with a surface (e.g., peripheral surface) of
the first coolant duct 502, shown in FIG. 5. In this way, the
contacted area between the fins and the coolant ducts is increased,
thereby increasing the heat transfer capacity of the heat
exchanger. Again the fin structure 510 includes a plurality of
stacked layers forming a plurality of repeating offset cells
structures, discussed in greater detail with regard to FIG. 7.
[0050] FIG. 7 shows a portion 700 of the fin structure 510 shown in
FIGS. 5 and 6. The fin structure 510 includes a plurality of
stacked layers of fins including a first layer of fins 710 and a
second layer of fins 712 forming cell structures 702. The cell
structures 702 have a square cross-section. The cutting plane for
the cross-sections is perpendicular to a lateral axis. A
longitudinal axis and a transverse axis are also provided for
reference. Furthermore, due to the offset between the cells
structures cells in non-peripheral sections of the structure each
flows air to two downstream cell structures and/or receives air
from two upstream cell structures. In this way, a large number of
flow paths are formed in the fin structure, thereby increasing
turbulence in the fin structure as well as making it less
susceptible to large drops in airflow through the cell structures
caused by damaged fins and/or blocked cells.
[0051] Additionally, each fin in the fin structure further includes
laterally-peripheral edges. The laterally-peripheral edges 730 of
fins in the first layer of fins 710 are in contact with
laterally-peripheral edges 732 of fins in the second layer of fins
712. The edges (730 and 732) are parallel to one another. However,
other orientations have been contemplated.
[0052] The first layer of fins 710 is offset by half the lateral
width of one of the cells included in the layer of fins from the
second layer of fins 712. However, other degrees of offset have
been contemplated. For example, the first layer of fins may be
offset by a quarter of the lateral width of the cells from the
second layer of fins.
[0053] FIG. 8 shows a fin 800 included in the fin structure 510
shown in FIG. 7. The fin 800 includes a plurality of consecutively
arranged planar surfaces 802. The fin 800 define a plurality of
square air-flow channels 804 bounded by three consecutively
arranged planar sides in the fin 800. It will be appreciated that
when fin 800 is coupled with adjacent fins in a set of stacked
fins, the square air-flow channels are bounded by four planar
sides. An angle 806 is formed between consecutively arranged planar
surfaces. The angle 806 is 90 degrees, in the depicted example.
Therefore, the consecutively arranged planar surfaces are
perpendicular to one another.
[0054] FIGS. 9 and 10 show another example of a heat exchanger 900
that may be included in the vehicle system 10 shown in FIG. 1.
Thus, the heat exchanger 900 may be the heat exchanger 50, shown in
FIG. 1, in some examples.
[0055] FIG. 9 shows the heat exchanger 900 having a first coolant
duct 902, a second coolant duct 904, and a fin structure 906
extending between the coolant ducts. FIG. 10 shows the heat
exchanger 900 without the first coolant duct 902, exposing a
greater viewable portion of the fin structure 906. As shown, the
fin structure 906 is arranged at a non-straight angle 1001 with
regard to an axis 1000 parallel to a plurality of the planar
surfaces in the fin structure and a general direction 1002 of
airflow entering the fin structure. Specifically, the angle 1001 is
15.degree.. However, other angles have been contemplated.
[0056] FIG. 11 shows a detailed view of a portion 1100 of the fin
structure 906 shown in FIGS. 9 and 10. As illustrated, a leading
layer of fins 1102 (e.g., a peripheral layer of fins) is tapered to
accommodate for the non-straight orientation (e.g., 15.degree.
alignment) of the fin structure. The leading layer of fins includes
a plurality of stacked fins. Each of the fins may be similar in
size and geometry and are longitudinally and laterally aligned. It
will be appreciated that a trailing set of fins may also be tapered
to accommodate the non-straight orientation of the fin structure
with regard to the orientation of the coolant conduits (902 and
904) shown in FIGS. 9 and 10. Therefore, the leading and trailing
layers of fins are tapered and each of the cells in the leading and
trailing layers of fins have unequal cell sizes. Specifically, the
lateral width of the cells in the set of leading and trailing fins
varies in a longitudinal direction. The portion 1100 of the fin
structure shown in FIG. 11 also includes a second layer of fins
1104 offset from the leading layer of fins 1102. Additionally, the
leading layer of fins 1102 includes a plurality of cells 1106.
[0057] In another example, the fin structure may comprise a pyramid
type structure including four or five faces with edges comprised of
small metal structures such as thin bars or rods. It will be
appreciated that a pyramid type structure may also create a
desirable amount of turbulent airflow in the heat exchanger. FIG.
13 shows an example pyramid type structure 1300 including a
plurality of rods 1302. The rods may have a circular cross-section
or an oval cross-section in some examples. The rods 1302 may be
coupled to one another to form triangular cells 1304. A portion of
the triangular cells 1304 may be orientated in a transverse and
longitudinal direction and another portion of the cells may be
orientated in a lateral and longitudinal direction. It will be
appreciated that the pyramid type structure 1300 may be coupled to
coolant conduits. Specifically, the structure 1300 may interpose
two coolant conduits.
[0058] FIG. 14 shows a method 1400 for operation of a heat
exchanger. The method may be implemented via one or more of the
heat exchangers disclosed in FIG. 1-13 or may be implemented via
another suitable heat exchanger.
[0059] At 1402 the method includes flowing coolant through a first
coolant duct and a second coolant duct. Next at 1404 the method
includes flowing turbulent air through a plurality of repeating
offset cell structures formed by a plurality of stacked layers of
fins, each fin including a repeated pattern of folds. In one
example, the airflow through the plurality of repeating offset cell
structures is isotropically turbulent. In another example, the
offset cell structures are arranged at a non-straight angle with
regard to an outlet direction of a fan.
[0060] Note that the example routines included herein can be used
with various engine and/or vehicle system configurations. As such,
various acts, operations, or functions illustrated may be performed
in the sequence illustrated, in parallel, or in some cases omitted.
Likewise, the order of processing is not necessarily required to
achieve the features and advantages of the example embodiments
described herein, but is provided for ease of illustration and
description. One or more of the illustrated acts or functions may
be repeatedly performed depending on the particular strategy being
used.
[0061] It will be appreciated that the configurations and methods
disclosed herein are exemplary in nature, and that these specific
embodiments are not to be considered in a limiting sense, because
numerous variations are possible. For example, the above technology
can be applied to V-6, I-4, I-6, V-12, opposed 4, and other engine
types. The subject matter of the present disclosure includes all
novel and non-obvious combinations and sub-combinations of the
various systems and configurations, and other features, functions,
and/or properties disclosed herein.
[0062] The following claims particularly point out certain
combinations and sub-combinations regarded as novel and
non-obvious. These claims may refer to "an" element or "a first"
element or the equivalent thereof. Such claims should be understood
to include incorporation of one or more such elements, neither
requiring nor excluding two or more such elements. Other
combinations and sub-combinations of the disclosed features,
functions, elements, and/or properties may be claimed through
amendment of the present claims or through presentation of new
claims in this or a related application. Such claims, whether
broader, narrower, equal, or different in scope to the original
claims, also are regarded as included within the subject matter of
the present disclosure.
* * * * *