U.S. patent application number 10/592355 was filed with the patent office on 2007-08-30 for stacked-plate heat exchanger.
This patent application is currently assigned to BEHR GmbH & CO. KG. Invention is credited to Jens Richter.
Application Number | 20070199687 10/592355 |
Document ID | / |
Family ID | 38442895 |
Filed Date | 2007-08-30 |
United States Patent
Application |
20070199687 |
Kind Code |
A1 |
Richter; Jens |
August 30, 2007 |
Stacked-Plate Heat Exchanger
Abstract
The invention relates to a stacked-plate heat exchanger,
particularly an in-tank oil cooler, which is mounted in a coolant
casing of a coolant cooler for vehicles. The heat exchanger
comprises a number of stacked and interconnected, particularly
soldered, elongated plates (71-77), each consisting of two plate
halves and enclosing a hollow space though which a medium to be
cooled, such as oil, passes in a longitudinal direction of the
plates. In order to create a stacked-plate heat exchanger that can
be economically produced, each of the plate halves have a multitude
of grooves extending from one longitudinal side to the opposite
longitudinal side of the plate half.
Inventors: |
Richter; Jens;
(Grossbottwar, DE) |
Correspondence
Address: |
FOLEY AND LARDNER LLP;SUITE 500
3000 K STREET NW
WASHINGTON
DC
20007
US
|
Assignee: |
BEHR GmbH & CO. KG
|
Family ID: |
38442895 |
Appl. No.: |
10/592355 |
Filed: |
March 4, 2005 |
PCT Filed: |
March 4, 2005 |
PCT NO: |
PCT/EP05/02317 |
371 Date: |
September 11, 2006 |
Current U.S.
Class: |
165/153 ;
165/916 |
Current CPC
Class: |
F28D 1/0325 20130101;
F28D 2021/0089 20130101; F28D 1/053 20130101; F28F 9/0234
20130101 |
Class at
Publication: |
165/153 ;
165/916 |
International
Class: |
F28D 1/02 20060101
F28D001/02 |
Foreign Application Data
Date |
Code |
Application Number |
Mar 11, 2004 |
DE |
10 2004 012 392.2 |
Claims
1. A stacked-plate heat exchanger, in particular in-tank oil
cooler, which is installed in a coolant box of a coolant cooler,
for motor vehicles, with a plurality of elongate plates which are
stacked one on the other and are connected, in particular soldered,
to one another and which are composed in each case of two plate
halves and surround a cavity for leading through a medium to be
cooled, such as oil, in the longitudinal direction of the plates,
wherein each of the plate halves has a multiplicity of grooves
which run from one longitudinal side of the plate half to its
opposite longitudinal side.
2. The stacked-plate heat exchanger as claimed in claim 1, wherein
the elongate plates are composed in each case of two identical
plate halves rotated through 180.degree. with respect to one
another.
3. The stacked-plate heat exchanger as claimed in claim 1, wherein
the grooves run rectilinearly from one longitudinal side of the
plate half to its opposite longitudinal side.
4. The stacked-plate heat exchanger as claimed in claim 1, wherein
the grooves are embossed on one side in each plate half.
5. The stacked-plate heat exchanger as claimed in claim 1, wherein
the grooves are delimited on the longitudinal sides by a peripheral
edge.
6. The stacked-plate heat exchanger as claimed in claim 1, wherein
a plate is formed by two plate halves which bear against one
another and the grooves of which are embossed outwardly.
7. The stacked-plate heat exchanger as claimed in claim 1, wherein
two plates bear against one another and are soldered to one another
with their raised regions formed by the grooves.
8. The stacked-plate heat exchanger as claimed in claim 1, wherein
the grooves run at an angle of 35.degree. to 55.degree., in
particular of 45.degree., with respect to the longitudinal axis of
the associated plate half.
9. The stacked-plate heat exchanger as claimed in claim 1, wherein
the grooves of two plate halves bearing against one another are
arranged at an angle of 70.degree. to 110.degree., in particular of
90.degree., with respect to one another.
10. The stacked-plate heat exchanger as claimed in claim 1, wherein
the grooves have a depth of 0.5 to 1.5 mm, in particular of 1.15
mm.
11. The stacked-plate heat exchanger as claimed in claim 1, wherein
the grooves of a plate half are arranged parallel to one another at
a distance of 3 to 5 mm, in particular of 4 mm, from one
another.
12. The stacked-plate heat exchanger as claimed in claim 1, wherein
the plate halves have a width of about 20 to 120 mm, in particular
of 20 to 50 mm.
13. The stacked-plate heat exchanger as claimed in claim 1, wherein
the hydraulic diameter has a value of 1.5 to 2.5 mm, in particular
of 1.8 mm.
14. The stacked-plate heat exchanger as claimed in claim 1, wherein
the plate halves are formed from a metallic material, in particular
from aluminum or high-grade steel.
15. The stacked-plate heat exchanger as claimed in claim 14,
wherein at least one side of the plate halves is coated with
soldering aid material.
16. The stacked-plate heat exchanger as claimed in claim 1, wherein
the plate halves have in each case a pair of throughholes as inflow
lines and outflow lines.
17. The stacked-plate heat exchanger as claimed in claim 16,
characterized in that the edge region of the throughholes is of
raised design.
18. The stacked-plate heat exchanger as claimed in claim 16,
wherein embossings are provided in the edge region of the
throughholes.
19. The stacked-plate heat exchanger as claimed in claim 18,
wherein, as seen in section, the embossings are of wavy design with
wave crests and wave troughs.
20. The stacked-plate heat exchanger as claimed in claim 19,
wherein a plurality of plate halves are soldered essentially
linearly to the in each case adjacent plate halves both on their
inside and on their outside.
21. The stacked-plate heat exchanger as claimed in claim 19,
wherein, as seen in a top view, the embossings run in a
meander-like manner at least partially around the throughholes.
22. The stacked-plate heat exchanger as claimed in claim 1, wherein
in each case two plate halves are connected to one another in one
piece by means of a bending edge running in the longitudinal
direction or in the transverse direction, in order to form a
conduction device for the medium to be cooled.
23. The stacked-plate heat exchanger as claimed in claim 22,
wherein the conduction device is formed by an essentially
rectangular panel which is subdivided by means of the bending edge
into two elongate halves which are folded together.
24. The stacked-plate heat exchanger as claimed in claim 23,
wherein the panel has a peripheral edge which is raised with
respect to the panel surface.
25. The stacked-plate heat exchanger as claimed in claim 24,
wherein the peripheral edge is interrupted at the intersection
points with the bending edge.
26. The stacked-plate heat exchanger as claimed in claim 24,
wherein the two panel halves bear against one another with the
peripheral edge in the folded-together state.
27. A motor vehicle cooler with at least one waterbox, wherein a
stacked-plate heat exchanger as claimed in claim 1 is installed in
the waterbox.
Description
[0001] The invention relates to a stacked-plate heat exchanger, in
particular an in-tank oil cooler, for motor vehicles, with a
plurality of elongate plates which are stacked one on the other and
are connected, in particular soldered, to one another and which are
composed in each case of two identical plate halves rotated through
180.degree. with respect to one another and surround a cavity for
leading through a medium to be cooled, such as oil, in the
longitudinal direction of the plates.
[0002] German laid-open publication DE 43 08 858 C2 discloses a
plate heat exchanger with plates which are stacked one on the other
and are soldered to one another and which are composed of two
identical plate halves rotated through 180.degree. with respect to
one another and surround a cavity for the conduction of a medium to
be cooled. The plate halves are provided with an embossed edge for
soldering the plate halves to form a plate and with connection
faces for soldering the plates to one another. Moreover, the plate
halves are provided on the inside and on the outside with
frustoconical embossings. The plate halves are configured
mirror-symmetrically with respect to their transverse and/or
longitudinal axis. The frustoconical embossings are arranged in the
manner of a checkerboard between the connection faces. Positive
embossings alternate with negative embossings. The positive
embossings and the negative embossings are of knob-like design. In
the assembled state, the plate halves surround a cavity through
which a fluid, for example oil, flows. The knobs projecting into
this cavity are intended to ensure a good swirling of the oil and,
as a result of their tie rod function, to increase the
strength.
[0003] The object of the invention is to provide a stacked-plate
heat exchanger, in particular an in-tank oil cooler, for motor
vehicles, with a plurality of elongate plates which are stacked one
on the other and are connected, in particular soldered, to one
another and which are composed in each case of two identical plate
halves rotated through 180.degree. with respect to one another and
surround a cavity for leading through a medium to be cooled, such
as oil, in the longitudinal direction of the plates, which
stacked-plate heat exchanger is of simple construction and can be
produced cost-effectively. The stacked-plate heat exchanger
according to the invention is nevertheless to ensure good swirling
of the medium to be cooled in the cavity formed between the plate
halves.
[0004] In a stacked-plate heat exchanger, in particular an in-tank
oil cooler, for motor vehicles, with a plurality of elongate plates
which are stacked one on the other and are connected, in particular
soldered, to one another and which are composed in each case of two
plate halves and surround a cavity for leading through a medium to
be cooled, such as oil, in the longitudinal direction of the
plates, the object is achieved in that each of the plate halves has
a multiplicity of grooves which run from one longitudinal side of
the plate half to its opposite longitudinal side. The plates are
also designated as flat tubes or panels. The run of the grooves
ensures the passage of coolant from one longitudinal side of the
plate half to the opposite longitudinal side. In the cavity, the
grooves ensure a good swirling of the medium to be cooled.
[0005] A preferred exemplary embodiment of the stacked-plate heat
exchanger is characterized in that the elongate plates are composed
in each case of two identical plate halves rotated through
180.degree. with respect to one another. The production of the
stacked-plate heat exchanger according to the invention is thereby
simplified considerably.
[0006] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the grooves
run rectilinearly from one longitudinal side of the plate half to
its opposite longitudinal side. This ensures an unimpeded passage
of coolant from one longitudinal side of the plate half to the
opposite longitudinal side.
[0007] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the grooves
are embossed on one side in each plate half. The grooves are formed
by rectilinear, elongate, narrow depressions which are embossed on
one side, for example, in a sheet metal material. Since the grooves
are embossed on only one side, the production of the plate halves
is simplified.
[0008] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the grooves
are delimited on the longitudinal sides by a peripheral edge. The
peripheral edge serves for connecting, in particular soldering, two
plate halves to one another. The cavity between the two plate
halves is thereby sealed off with respect to the surroundings.
[0009] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that a plate is
formed by two plate halves which bear against one another and the
grooves of which are embossed outwardly. The grooves delimit,
inside the plate, the flow path of the medium to be cooled.
Preferably, an inlet for the medium to be cooled is provided at one
end of the plate and an outlet for said medium is provided at the
other end of the plate.
[0010] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that two plates
bear against one another with their raised regions formed by the
grooves and are connected to one another by means of a soldering
process. Coolant, for example water, can pass between the raised
regions from one longitudinal side of the respective plate half to
its opposite longitudinal side. Moreover, the plates are equipped
in the edge region of throughholes with cup-shaped raised regions
at which the plates are likewise soldered to one another.
[0011] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the grooves
run at an angle of 35.degree. to 55.degree., in particular of
45.degree., with respect to the longitudinal axis of the associated
plate half. This ensures, on the one hand, that the medium to be
cooled can flow from one end of the plate to the other end through
the cavity formed inside the plate. On the other hand, the run
according to the invention of the grooves also ensures that the
coolant can flow in two plates from one longitudinal side to the
opposite longitudinal side.
[0012] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the grooves
of two plate halves bearing against one another are arranged at an
angle of 70.degree. to 110.degree., in particular of 90.degree.,
with respect to one another. This provides, inside the plates, for
the medium to be cooled a flow path which has many changes of
direction and vortices. The advantage of this is that boundary
layers which form in the cavity during operation are repeatedly
broken up. This leads to a greatly diluted heat transition, as
compared with a smooth duct without grooves. Thus, when it flows
through the cavity, the medium to be cooled is subjected to many
changes of direction. By contrast, the coolant can flow, virtually
unimpeded and rectilinearly, through the grooves between two plates
bearing against one another. The angle of 90.degree. produces a
virtually circular soldering meniscus at the connection point of
the two grooves. The flow longitudinally and transversally with
respect to the main flow direction of the medium to be cooled is
thereby influenced identically. The angle is preferably 80.degree.
to 100.degree..
[0013] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the grooves
have a depth of 0.8 to 1.5 mm, in particular of 1.15 mm. This depth
has proved to be particularly advantageous within the scope of the
present invention. Particularly in the case of fuel coolers, the
grooves preferably have a depth of 0.5 mm to 1.5 mm.
[0014] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the grooves
of a plate half are arranged parallel to one another at a distance
of 3 to 5 mm, in particular of 4 mm, from one another. This
division dimension has proved to be particularly advantageous
within the scope of the present invention.
[0015] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the plate
halves have a width of about 20 to 50 mm.
[0016] This width has proved to be particularly advantageous within
the scope of the present invention. In commercial vehicles, the
plate halves preferably have a width of about 20 to 120 mm. A width
of 70 to 80 mm, in particular of 76 mm, is particularly
preferred.
[0017] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the hydraulic
diameter has a value of 1.5 to 2.5 mm, in particular of 1.8 mm.
This value has proved to be particularly advantageous within the
scope of the present invention.
[0018] The hydraulic diameter between two adjacent plate halves
along the main flow direction of the medium to be cooled
constitutes the ratio between the throughflow duct cross section
and the heat exchange area. The hydraulic diameter is defined as
the quadruple of the ratio of the area ratio to the area density.
The area ratio is determined as the ratio of the free duct cross
section to the overall end face area of the duct between two
adjacent plate halves. The area density is determined from the
ratio of the heat-transmitting area to the block volume. The
hydraulic diameter should preferably remain as constant as possible
over the entire main flow direction of the medium to be cooled. A
uniform throughflow capacity of the cavity between two plate halves
is thereby achieved.
[0019] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the plate
halves are formed from a metallic material, in particular from
aluminum or high-grade steel. The plates are preferably connected
to one another by hard soldering. High-grade steel is preferably
used in commercial vehicles.
[0020] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that at least one
side of the plate halves is coated with soldering aid material. The
process of producing the stacked-plate heat exchanger according to
the invention can thereby be simplified.
[0021] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the plate
halves have in each case a pair of throughholes as inflow lines and
outflow lines. The medium to be cooled passes via the throughholes
into the cavity between two plate halves forming a plate or a flat
tube. The plates may also be designated as panels and the plate
halves as panel halves.
[0022] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the edge
region of the throughholes is of raised design. Preferably, the
edge region of the throughholes is raised to exactly the same
extent as the grooves or corrugations. Two raised edge regions,
bearing against one another, of different plate halves seal off the
throughholes and the cavity between two plate halves, which is
connected to the throughholes, with respect to the surroundings
through which coolant flows.
[0023] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that embossings
are provided in the edge region of the throughholes. The embossings
serve for reinforcing the plate halves in the region of the
throughholes.
[0024] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that, as seen in
section, the embossings are of wavy design in the inlet region with
wave crests and wave troughs.
[0025] The wave crests and wave troughs provide essentially
punctiform contacts between two adjacent plate halves.
[0026] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that a plurality
of plate halves are soldered in the inlet region essentially
linearly to the in each case adjacent plate halves both on their
inside and on their outside. The internal pressure resistance of
the tubes formed in each case from two plate halves thereby rises
sharply.
[0027] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that, as seen in a
top view, the embossings run in a meander-like manner at least
partially around the throughholes. The contact area between two
plate halves in each case is thereby increased.
[0028] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that in each case
two plate halves are connected to one another in one piece by means
of a bending edge running in the longitudinal direction or in the
transverse direction, in order to form a conduction device for the
medium to be cooled. Since the two plate halves are already
connected in one piece to one another at the bending edge, they
merely have to be soldered to one another on one side. The cross
section through which the medium to be cooled flows is thereby
increased. Furthermore, the number of individual parts required is
reduced by half, since only one part is required for each
conduction device.
[0029] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the
conduction device is formed by an elongate, in particular
essentially rectangular, panel which is subdivided by means of the
bending edge into two elongate halves which are folded together.
The panel is preferably an embossed stamping consisting of a
metallic material which can be produced simply and
cost-effectively. In the folded-together state, the panel halves
lie congruently one on the other.
[0030] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the panel has
a peripheral edge which is raised with respect to the panel
surface. Preferably, the panel is embossed within the peripheral
edge, the depth of the embossed face amounting to half the clear
width of the conduction device.
[0031] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the
peripheral edge is interrupted at the intersection points with the
bending edge. In the region of the bending edge, the panel has the
same depth over the entire length of the bending edge. This avoids
undesirable damage to the panel material in the region of the
bending edge during the folding-together operation.
[0032] A further preferred exemplary embodiment of the
stacked-plate heat exchanger is characterized in that the two panel
halves bear against one another with the peripheral edge in the
folded-together state. The panel halves are preferably soldered to
one another at the peripheral edge.
[0033] In a vehicle cooler with at least one waterbox, the object
specified above is achieved in that a stacked-plate heat exchanger
described above is installed in the waterbox.
[0034] Further advantages, features and particulars of the
invention may be gathered from the following description in which
an exemplary embodiment is described in detail with reference to
the drawing. In this case, the features mentioned in the claims and
in the description may be essential to the invention in each case
individually in themselves or in any desired combination. In the
drawing:
[0035] FIG. 1 shows a perspective illustration of a plate half;
[0036] FIG. 2 shows a bottom view of one end of the plate half from
FIG. 1;
[0037] FIG. 3 shows a sectional view along the line III-III in FIG.
2;
[0038] FIG. 4 shows a perspective illustration of two plate
halves;
[0039] FIG. 5 shows an enlarged detail from FIG. 4;
[0040] FIG. 6 shows a perspective illustration of seven plates
which are assembled to form a stacked-plate heat exchanger
according to the invention;
[0041] FIG. 7 shows an enlarged perspective illustration of a
closing-off plate of the stacked-plate heat exchanger illustrated
in FIG. 6;
[0042] FIG. 8 shows a cross-sectional view through one end of the
stacked-plate heat exchanger illustrated in FIG. 6;
[0043] FIG. 9 shows a side view of one end of the stacked-plate
heat exchanger illustrated in FIG. 6;
[0044] FIG. 10 shows a perspective illustration of a waterbox with
an installed stacked-plate heat exchanger;
[0045] FIG. 11 shows a cooler with an installed waterbox, such as
is illustrated in FIG. 10;
[0046] FIG. 12 shows an illustration of the soldering menisci in a
duct section;
[0047] FIG. 13 shows an illustration of a top view of virtually
circular soldering menisci;
[0048] FIG. 14 shows a top view of a stacked-plate heat exchanger
according to a further exemplary embodiment of the invention;
[0049] FIG. 15 shows a side view of the stacked-plate heat
exchanger from FIG. 14;
[0050] FIG. 16 shows a sectional view along the line XVI-XVI in
FIG. 14;
[0051] FIG. 17 shows a sectional view along the line XVII-XVII in
FIG. 14;
[0052] FIG. 18 shows a sectional view along the line XVIII-XVIII in
FIG. 14;
[0053] FIG. 19 shows an enlarged illustration of the detail XIX
from FIG. 14;
[0054] FIG. 20 shows a top view of a conduction device according to
the invention in the folded-open state;
[0055] FIG. 21 shows the conduction device from FIG. 20 in the half
folded-together state;
[0056] FIG. 22 shows a top view of a stacked-plate heat exchanger
with a closed conduction device, such as is illustrated in FIGS. 20
and 21, in the closed state;
[0057] FIG. 23 shows a side view of the stacked-plate heat
exchanger from FIG. 22, and
[0058] FIG. 24 shows a sectional view along the line XXIV-XXIV in
FIG. 22.
[0059] FIG. 1 illustrates a plate half 1 in perspective. The plate
half 1 has the configuration of an elongate panel consisting of
sheet aluminum with two straight longitudinal sides 2 and 3 which
are arranged parallel to one another. The plate half 1 is rounded
semicircularly at its ends 4 and 5. Throughholes 8 and 9 are
provided in the ends 4 and 5. The edge regions 10, 11 of the
throughholes 8, 9 are embossed in a recessed manner, so that the
edge regions 10, 11 are raised on the underside of the plate half
1.
[0060] A multiplicity of grooves 12 are embossed in the plate half
1 between the throughholes 8 and 9. The grooves 12 run
rectilinearly from one longitudinal side 2 of the plate half 1 to
its opposite longitudinal side 3. The grooves have the
configuration of elongate depressions which are raised on the
underside of the plate half 1. However, the grooves may also run
nonrectilinearly, for example in a wavy or zigzag-shaped
manner.
[0061] FIG. 2 illustrates a bottom view of the end 4 of the plate
half 1 from FIG. 1. The edge region 10 and ten grooves 21 to 30 are
raised out of the drawing plane. The ends of the grooves 21 to 30
are rounded toward the longitudinal sides 2, 3. The longitudinal
axis of the plate half 1 is designated by 31. The grooves 21 to 30
are arranged at an angle .alpha. of 45.degree. with respect to the
longitudinal axis 31.
[0062] In FIG. 3, it can be seen that, as seen in cross section,
the plate half 1 has a wavy profile. The wavy cross-sectional
profile is formed by the grooves which are embossed on one side in
the plate half 1.
[0063] FIG. 4 illustrates two plate halves 1 and 42 in perspective.
The sides of the plate halves 1 and 42 on which the grooves are
raised face away from one another.
[0064] In FIG. 5, it can be seen that the plate half 42 has exactly
the same configuration as the plate half 1.
[0065] However, the plate half 42 is arranged so as to be rotated
through 180.degree. with respect to the plate half 1. One end 44
with a throughhole 48, the edge region 50 of which is raised out of
the drawing plane, is arranged above the throughhole 8 of the end 4
of the plate half 1, the cup-shaped edge region 10 of the
throughhole 8 being raised into the drawing plane. Grooves 52 which
are raised out of the drawing plane are formed in the plate half
42. The grooves 52 are arranged at an angle .beta. of 90.degree.
with respect to the grooves 12 which are raised into the drawing
plane. The two plate halves 1 and 42 are soldered to one another at
the contact points of the grooves and in the edge regions 2 and 3
so as to form a plate or a flat tube.
[0066] In FIG. 6, a multiplicity of plates 60 are soldered to one
another. The throughholes of the plates 60 are closed on the
underside by means of closing-off plates 61, 62. On the top side of
the plates 60, connection pieces 67, 68 are placed onto the
throughholes at the ends. The medium to be cooled can be introduced
through one of the connection pieces 67, 68 into the interior of
the plates 60. The medium to be cooled can emerge from the plates
60 out of the other connection piece 68, 67.
[0067] FIG. 7 illustrates the closing-off plate 61 in an enlarged
perspective view. The closing-off plate 61 has the configuration of
a circular plate 64 which has a circular central elevation 65. The
outside diameter of the circular elevation 65 is adapted to the
inside diameter of the associated throughhole of the respective
plate.
[0068] In FIGS. 8 and 9, it can be seen that the stacked-plate heat
exchanger illustrated in perspective in FIG. 6 comprises seven
plates 71 to 77 which are stacked one above the other. Inside the
plates 71 to 77, a multiplicity of essentially zigzag-shaped flow
paths for the medium to be cooled are formed, which run between the
plates 71 to 77 rectilinearly through the recessed regions in each
case between two grooves from one side of the corresponding plate
half to its opposite side.
[0069] FIG. 10 illustrates a waterbox 78 in which the stacked-plate
heat exchanger illustrated in FIG. 6 is installed. The plates 60
are arranged within the waterbox 78. The connection pieces 67, 68
project out of the waterbox 78.
[0070] In FIG. 11, the waterbox 78 from FIG. 10 is built onto one
side of a cooling network 79. A further waterbox 80 is built onto
the other side of the cooling network 79. The two waterboxes 78 and
80 and the cooling network 79 together form a coolant cooler 81 for
a motor vehicle (not illustrated).
[0071] The profiling of the plate halves 1 and 42 is designed such
that the wavy profiles are in punctiform contact with one another
when the plates are laid one onto the other. This repeatedly
results, inside the plates, in changes of direction for the medium
to be cooled which flows through. The multiplicity of contact
points at which the two plate halves are soldered to one another
ensures good pressure stability. The leg angle of the profiling is
45.degree. with respect to the main flow direction of the medium to
be cooled. The hydraulic diameter amounts to 1.8 mm. The embossing
angle is in a range of between 20.degree. and 60.degree. with
respect to the main flow direction. The hydraulic diameter may vary
between 1.5 mm and 2.5 mm.
[0072] The large-area embossing in the inlet and outlet region
makes it possible to have a leaktight plate connection, without
additional components having to be used. The plate halves have
horizontal soldering faces, thus ensuring a sufficient flow passage
of the coolant on the outside of the cooler. The plate halves are
preferably angled slightly at their peripheral edge. The planeness
of the plate in the unsoldered state is thereby improved. The edge
angle is between 5.degree. and 20.degree., preferably 10.degree..
The plate halves consist of aluminum and are connected to one
another by means of a wheel-soldering process.
[0073] In FIG. 12, it can be seen that in each case two plate
halves are connected to one another by means of soldering menisci
101, 102 and 103, 104. In FIG. 13, it can be seen that the
soldering menisci 101 to 104 are of virtually circular design, as
seen in a top view.
[0074] FIG. 14 illustrates a plate half 1 of a stacked-plate heat
exchanger according to the invention in a further exemplary
embodiment. The same reference symbols as in the exemplary
embodiment illustrated in FIG. 1 are used to designate identical
parts. In order to avoid repetitions, reference is made to the
preceding description of FIG. 1. Only the differences between the
exemplary embodiments are dealt with below.
[0075] In the plate half 1 illustrated in FIG. 14, the edge regions
110, 111 of the throughholes 8, 9 are provided with embossings. The
edge region 111 at the end 5 of the plate half 1 has meander-like
embossings 115 and 116 which are connected by means of a connecting
bead 117. The edge region 110 at the end 4 of the plate half 1 has
meander-like embossings 118 and 119 which are connected to one
another by means of a connecting bead 120. In each case two plate
halves 1, such as are illustrated in FIG. 14, are, as described
above, soldered to one another at the contact points of the grooves
12 and in the edge regions 2 and 3 and also at the embossings 118,
119 so as to form a plate or a flat tube which is also designated
as a conduction device.
[0076] FIG. 15 illustrates a side view of a cooler block which
comprises a plurality of flat tubes stacked one above the
other.
[0077] FIG. 16 illustrates a sectional view along the line XVI-XVI
in FIG. 14. In the sectional view, it can be seen that various flat
tubes of a cooler block are connected linearly to one another in a
stacked type of construction in the region of the meander-like
embossings 115, 116 and at the embossings 118, 119.
[0078] FIG. 17 illustrates a sectional view along the line
XVII-XVII in FIG. 14. In the sectional illustration, it can be seen
that the number of essentially linear contact faces is increased as
a result of the meander-like embossings 116. The meander-like
embossings 116 are also designated as reinforcing beads. It can be
seen here how the embossings at the plate end are soldered to one
another both on the inside and on the outside of the stacked-plate
heat exchanger.
[0079] FIG. 18 illustrates a sectional view along the line
XVIII-XVIII in FIG. 14. It can be seen here how the embossings 119
at the plate end 4 are soldered to one another both on the inside
and on the outside of the stacked-plate heat exchanger.
[0080] FIG. 19 shows an enlarged illustration of the detail XIX
from FIG. 14. The form of the embossings 118, 119 is designed such
that plates stacked one above the other are soldered to one another
linearly both on the inside and on the outside. The internal
pressure resistance of a tube formed from two plate halves thereby
rises sharply. The plate connections are illustrated in a
meandering manner in FIG. 19.
[0081] FIG. 20 illustrates a conduction device 140, which is also
designated as a flat tube or short tube, in the folded-open state.
The flat tube 140 is formed by a panel 142 which has essentially
the configuration of a rectangle, the corners of which are rounded.
The panel 142 is a stamping consisting of sheet aluminum having a
bending edge 143, by means of which the panel 142 is subdivided in
the longitudinal direction into two halves 145, 146 of identical
size which are also designated as plate halves. The two plate
halves 145, 146 correspond, apart from their one-piece design, to
the plate halves of the preceding exemplary embodiments. The panel
142 is delimited on the outside by a peripheral edge 148 which
serves for soldering the two panel halves 145, 146 to one another
in the folded-together state. Within the peripheral edge 148, the
panel halves 145, 146 are provided with embossed grooves, such as
are described above.
[0082] FIG. 21 illustrates the tube 140 in the partly closed
state.
[0083] FIG. 22 illustrates a top view of the tube 140 in the closed
state. The tube 140 is the uppermost flat tube of a stacked-plate
heat exchanger having a plurality of flat tubes stacked one above
the other.
[0084] FIG. 23 illustrates a side view of the stacked-plate heat
exchanger from FIG. 22. In the side view, it can be seen that the
stacked-plate heat exchanger also comprises, in addition to the
flat tube 140, six further flat tubes 150 to 155 which are soldered
to one another in a stacked type of construction.
[0085] FIG. 24 illustrates a sectional view along the line
XXIV-XXIV in FIG. 22. In the sectional view, it can be seen that
the stacked-plate heat exchanger is formed from folded-together
flat tubes 140, 150 to 155. By the flat tubes being produced in one
piece, the number of parts necessary for constructing the
stacked-plate heat exchanger is reduced to half. The folded flat
tubes have the advantage that the length of the sealing solder seam
is reduced by virtually half.
* * * * *