Note: Descriptions are shown in the official language in which they were submitted.
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Tubing element for a heat exchanger means
Description
The present invention relates to a tubing element for a heat exchanger means,
a
heat exchanger means, the use of a tubing element to manufacture at least
partially a heat exchanger means, the use of a heat exchanger means to
exchange heat and the method of manufacturing of a tubing element.
In the technical field of heat exchangers such as evaporators, condensers,
radiators and coolers there have been many attempts to provide compact and
energy efficient heat exchangers. A heat exchanger is hereby generally known
to
provide for an exchange of thermal energy between a first medium such as, for
example, water and/or a cooling agent, and a second medium such as, for
example, air.
For instance, EP 1 840 494 A2 discloses a heat exchanger, whereby the heat
exchanger comprises a profile having two flat tubes with several channels and
whereby the tubes are connected by means of a bar. The profile is a one-piece
profile and may consist of aluminium or an aluminium alloy.
Moreover, DE 20 2008 006 379 U1 discloses an aluminium or aluminium alloy
profile, which can be used for tubes for heat exchangers. The profile has a
central channel and several further channels arranged around the central
channel.
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DE 2 209 325 discloses a tube for heat exchangers having a helical structure.
Furthermore, DE 2 209 329 discloses heat exchanger tubes having ribs on the
inner
side and the outer side of the tube.
Additionally GB 1 390 782 discloses a heat-exchange tubing having spaced metal
fins projecting inwardly of the tubing from the wall sections of the tubing
and
extending longitudinally of the tubing.
Further, EP 0 640 803 Al relates to heat transfer coil, where a second piece
of
tubing is wound around the first piece of tubing while the first piece is
straight and
where the first piece of tubing is then formed to define the overall coil
shape and
then the first and second pieces of tubing internally sized by internal
pressurization
to also force the two pieces of tubing to intimate contact with each other.
However, it is still desirable to improve the already known technical
solutions in the
field of heat exchangers.
It is therefore an object for the present invention to improve a tubing
element for a
heat exchanger means, a heat exchanger, the use of a tubing element to
manufacture at least partially a heat exchanger means, the use of a heat
exchanger
to exchange heat and a method of manufacturing of a tubing element, in
particular
in that the efficiency of the heat exchange is increased and that the overall
structure of the tubing element and the heat exchanger is improved and
simplified
and allows a more compact structure of a heat exchanger.
The above object is solved according to the present invention by a tubing
element
for a heat exchanger means with the features described herein. Accordingly, a
tubing element for a heat exchanger means is provided, the tubing element
being at
least partially a rigid elongated heat exchanger tubing having at least a
first end
and at least a second end and having a first side wall and a second side wall,
the
first side wall and the second side wall being arranged substantially parallel
to each
other and the distance between the first side wall and the second side wall
being
considerably smaller than the width of the first side wall and the second side
wall
resulting in a substantially overall flat tubing structure with connection
walls on
both sides, the tubing element having a plurality of fins on at
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least one of the outer surfaces of the first side wall and/or of the second
side
wall, wherein the fins have a defining angle Y enclosed by the fins and a
connection wall.
The tubing element having a plurality of fins on at least one of the outer
surfaces
of the first side wall and/or of the second side wall increases the tubing
element
surface for a better heat exchange between the said second medium, such as
air,
and the heat exchanger means.
The defining angle Y, enclosed by the fins and a connection wall, extends the
way of the heat exchange between the second medium and the surface of the
tubing element having a plurality of fins on at least one of the outer
surfaces of
the first side wall and/or of the second side wall. The plurality of fins
generate a
better air path along the fins and the tubing element. The fins can influence
the
direction of the air flow along the tubing element. Due to the orientation of
the
plurality of fins on at least one of the outer surfaces of the tubing element,
the
air flow along the tubing element at the heat exchanger means can be
controlled.
Such a tubing element for a heat exchanger means may be an elongated heat
exchanger microchannel tube. Such an elongated heat exchanger microchannel
tube may have a first and a second open end. There may be relatively large
parallel opposite side walls of the microchannel tube with generally flat
surfaces,
which are joined with relatively small opposite edge walls between the side
walls.
These edge walls may be convexly curved.
Heat transfer vapor or fluid may fill a heat exchanger microchannel tube and
may
flow from one end of the microchannel tube to the other end. The term
microchannel is also known as microport.
The said second medium such as air may flow around the outer sides of the
tubing element and may transport the heat from the tube away or vice versa.
By providing a plurality of fins on at least one of the outer surfaces of the
first
side wall and/or of the second side wall the surface for heat exchange is
increased. Thus, also the efficiency of the heat exchanger may be
significantly
improved.
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Moreover, it is possible that the width of the first side wall and the second
side
wall is approximately at least 10 times larger than the distance between the
first
side wall and the second side wall and/or that the first side wall and second
side
wall are connected respectively on both sides by a rounded connection wall.
Additionally, it is possible that the tubing element is at least partially
tilted or at
least partially tilted and sloped and at least partially helically wound
and/or
twisted so as to form at least a part of a helical structure, whereby
preferably the
helical structure has an overall cylindrical structure and/or that the helical
structure is formed in a cylindrical shape.
A tubing element having a tilted orientation also creates a tilted orientation
of the
fins which are grounded on at least one of the outer surfaces of the first
side wall
and/or of the second side wall.
The helical structure of the tubing element is determined merely by variables
radius r, angle a and angle p. Radius r defines the distance between the
center
of the tubing element and the central longitudinal axis X of the heat
exchanger
means. Angle a defines the slope of the tubing element and extends between the
central longitudinal axis X of the heat exchanger means and the central axis Z
of
the tubing element. Angle 13 defines the tilt of the tubing element and
extends
between the central longitudinal axis X of the heat exchanger means and the
central transversal axis Y of the tubing element.
Therefore, due to the tilted orientation of the tubing element, there are
almost
no horizontal surfaces on the tubing element within the heat exchanger means.
Natural condensate from air moisture disappears very quickly, because of the
tilted and at least partially helically wound and/or twisted tubing element.
Natural
condensate from air moisture disappears to the outside surface of the heat
exchanger means, because of the tilted orientation of the tubing element. So,
freezing of condensate from air moisture between each of said tubing elements
can be minimized.
Compared to the prior art, the tubing element, being at least partially tilted
and
at least partially helically wound and/or twisted so as to form at least a
part of a
helical structure, is more efficient with less material. Also the heat
exchanger
means needs a smaller volume in the whole heat exchanger system, due to the
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compact set of tubing elements. Making this heat exchanger a high power
density
solution with minimal volumetric footprint.
Further, this tubing element, being at least partially tilted and at least
partially
helically wound and/or twisted so as to form at least a part of a helical
structure,
effects a better interaction between the said second medium such as air and
the
surface of the tubing element, due to the tilted orientation of the tubing
element.
Furthermore, it is possible that the tubing element has a plurality of fins on
both
of the outer surfaces of the first side wall and of the second side wall. By
providing a plurality of fins on both of the outer surfaces of the first side
wall and
of the second side wall the advantage is achieved that the surface used for
the
heat exchange may be increased very easily and that the volume needed for the
tubing element is not increased substantially.
It is also possible that the fins are at least partially covered by a draining
plate
and/or that the fins are monoblock fins.
The fins may be substantially perpendicularly arranged on at least one of the
outer surfaces of the first side wall and/or of the second side wall.
Alternatively, the fins are inclined arranged on at least one of the outer
surfaces
of the first side wall and/or of the second side wall, whereby exemplarily the
angle between the fins and the outer surface is chosen within a range of
approximately 15 to 85 .
Additionally, the fins merely extend along the whole width of at least one of
the
outer surfaces of the first side wall and/or of the second side wall and/or
are
curved.
Furthermore, the fins may be arranged along a curve extending along the whole
width of at least one of the outer surfaces of the first side wall and/or of
the
second side wall and/or are curved, whereby between the fins being arranged
along a curve is a pitch and/or gap.
It is possible that the fins and/or the curve of fins and at least one of the
connection walls are arranged such to each other that they enclose an angle.
The
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angle may be substantially perpendicular. Alternatively, the angle may be
chosen
within range of about 15 to about 600 and is preferably chosen within a range
of
about 20 to about 25 . An angle of about 45 between the fins or the curve of
fins and at least one of the connection walls is considered to be
substantially
neutral, in particular as a neutral arrangement with respect to the
interference
with e.g. fans or the like, which might be connected or used together with a
heat
exchanger means comprising such a tubing element.
The fins and/or the curve of fins may be formed slightly concave or convex. In
particular, the slightly concave or convex shape of the fins may be achieved
by
an offset of the center part of the middle section of the fins and/or the
curve of
fins with respect to the endpoints of the fins and/or the curve of fins within
a
range of about 0.5 mm to about 5 mm, preferably of about 1 mm to about 2 mm,
most preferred of about 1.5 mm.
It is preferred that the fins are arranged such that the medium flowing
against
the fins flows against a concave formed part of the fin.
The fins may have a height chosen within a range of about 0.5 mm to about 5.0
mm, preferably about 2-3 mm.
Further, it is possible that the fins are arranged in a plurality of rows,
preferably
substantially parallel rows and/or preferably along at least a part of the
length of
the tubing element.
The tubing element may comprise at least one microchannel. Preferably several
microchannels with a round or circular cross-section and/or several
microchannels
with an angular cross-section, exemplarily several microchannels with a
triangular
cross-section and/or several microchannels with quadrangular cross-section are
provided.
At least some of the microchannels may be arranged with an off-set to each
other, whereby exemplarily all microchannels are arranged with an off-set to
each
other.
The off-set may result in several chamfers and/or grooves within the first
side
wall and/or the second side wall.
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Furthermore, the tubing element may comprise at its a first end and at its
second
end a collecting portion which is reducing the width of the first side wall
and the
second side wall to a smaller width.
Moreover, the present invention relates to a heat exchanger means having one
or
multiple tubing elements, as disclosed herein.
Additionally, the heat exchanger may comprise several tubing elements are
forming
as a substantially overall cylindrical structure having a central longitudinal
axis and
that the tubing elements are spirally curved around the central longitudinal
axis and
interleaved in the structure.
The heat exchanger means may be a radiator or a cooler or a condenser or an
evaporator.
Additionally, the present invention relates to the use of a tubing element to
manufacture a heat exchanger means with the features disclosed herein.
Accordingly, a tubing element is used to manufacture a heat exchanger means
exemplarily by tilting or by tilting and sloping and helically winding and/or
twisting
the tubing element so to form a part of a helical structure.
Moreover, the present invention relates to the use of a heat exchanger means
to
exchange heat with the features disclosed herein. Accordingly, a heat
exchanger
means is used as a radiator or as a cooler or as a condenser or as an
evaporator.
Furthermore, the present invention relates to a method of manufacturing of a
tubing
element with the features disclosed herein. Accordingly, a tubing element as
disclosed herein is manufactured, whereby exemplarily the tubing element is
received by using an extrusion process of a heat transfer material, whereby
preferably the extrusion process is a single extrusion process
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and/or whereby preferably the heat exchanger material is at least partially
aluminium or copper or an alloy thereof.
Further details and advantages of the present invention shall be described
hereinafter with respect to the drawings:
Fig. 1: A perspective view of tubing element according to the present
invention in a first embodiment;
Fig. 2: A perspective view of a tubing element according to a first
embodiment of the present invention;
Fig. 3: A further perspective view of the tubing element shown in Figure 2
showing the angles for the slope and the tilt of the tubing element;
Fig. 4: The perspective view shown in Figure 3 with further details;
Fig. 5: A perspective view of a tubing element according to the present
invention and as shown in Figure 2 together with connecting
elements;
Fig. 6: A side elevation of the tubing element as shown in Figures 2 to 5;
Fig. 7: A perspective view of a heat exchanger comprising a plurality of
tubing elements;
Fig. 8: A perspective view of a tubing element according to the present
invention in a second embodiment;
Fig. 9: A perspective view in detail of embodiment shown in Figure 8.
Fig. 10 a, b: The perspective view of a draining plate and the respective
tubing
element thereto; and
Fig. 11: A perspective view of a further embodiment of a heat exchanger
comprising the draining plate and the tubing element according to
Figures 10 a, b.
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Figure 1 shows the perspective view of a first embodiment of the tubing
element
10, however, without fins 60 or fins 60'.
The tubing element 10 is a rigid elongated heat exchanger tube having a first
end
20 and a second end 30. There are relatively large parallel opposite side
walls 40
and 50 with generally flat surfaces. The opposite parallel arranged side walls
40,
50 of the tubing element are joined with relatively small opposite edge walls
45,
55, which are rounded connection walls 45, 55. The tubing element 10 is
partially
tilted and sloped and also helically wound and twisted so as to form at least
a
part of a helical structure.
The distance d between the first side wall 40 and the second side wall 50 is
considerably smaller than the width W of the side walls 40, 50.
There are relatively large parallel opposite side walls 40 and 50 with
generally
flat surfaces. The opposite parallel arranged side walls 40, 50 of the tubing
element are joined with relatively small opposite edge walls 45, 55, which are
rounded connection walls 45, 55. The tubing element 10 is partially tilted and
sloped and also helically wound and twisted so as to form at least a part of a
helical structure.
The opposite side walls 40 and 50 of the heat exchanger microchannel tube 10
are oppositely disposed in general parallel planes in the helix within the
tube 10
there may be one or more media flow channels, which are formed between the
oppositely disposed side walls 40, 50. A heat transfer vapor or fluid such as
water
or oil or refrigerant fills the heat exchanger microchannel tube 10 and flows
from
one end 20 of the microchannel tube 10 to the other end 30. Preferably, the
resulting helix of the microchannel tube 10 is formed in a cylindrical shape.
Figure 2 shows a perspective view of a first embodiment of the tubing element
10. On both outer surfaces 42, 52 of the first side wall 40 and the second
side
wall 50 several fins 60 are arranged.
The fins 60 may be monoblock fins and are inclined arranged respective to the
outer surface 42, 52 of the first side wall 40 and a second side wall 50. The
angle
between the fins and the outer surface 42, 52 is 22.5 degrees in this example.
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The fins 60 merely extend along the whole width W of the outer surfaces 42, 52
of the first side wall 40 and the second side wall 50.
As can be seen e.g. in Figure 5 and 6, the fins 60 are slightly curved.
Figure 3 shows the defining angles, i.e. angle at defining a slope and angle
p1
defining the tilt. Furthermore, Figure 3 shows the defining axes X, Y and Z
and
also the radius r. The heat exchanger microchannel tube 10 may be
longitudinally
curved around the central axis X into a helix. This axis X is shown in Figure
3 and
is the central axis X of the overall and imaginary cylindrical shape of the
helix.
As can be seen in Figure 3, the fins 60 follow the slope and the tilt.
Angle al defining the slope is defined as the angle at between axis X and Z.
Angle 81 defining the tilt is defined as to angle 81 between axis X and Y. As
can
be seen in Figure 3, the radius r is the distance from axis X to the center of
the
angled finned tubing element 10 and/or to the intersection point of axis Y and
axis Z.
As can be further seen from Figure 4, the fins 60 have two defining angles Y
and
6. The angle Y is the angle which is enclosed by the fins 60 and the
connection
walls 45, 55 as also shown in Figures 2, 5 and 8. The angle 6 is the angle of
the
fin 60 and the outer surface 42, 52 of the first side wall 40 or the second
side
wall 50.
As can be seen from the further detail shown in Figure 4, the first distance a
between two adjacent fins 60 may be larger than a second distance b of these
adjacent fins 60. The first distance a may be used in the entry section of the
gap
defined by two adjacent fins 60, i.e. the section for the entry of a heat
transfer
media flowing through the fins. So, the fins 60 are substantially parallel.
The fins 60 according to the embodiment shown in Figures 2 to 6 are arranged
on
angles between 22.5 and 45 degrees to the outer surfaces 42, 52 of the first
side
wall 40 and of the second side wall 50.
This is, however, not mandatory. Alternatively, the fins 60 may be inclined
arranged on the at least one of the outer surfaces 42, 52 of the first side
wall 40
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and/or of the second side wall 50, whereby exemplarily the angle between the
fins 60 and the outer surface 42 or 52 may be chosen within a range of
approximately 15 to 85 .
The fins 60 merely extend along the whole width W of the outer surfaces 42, 52
of the first side wall 40 and/or of the second side wall 50 and are slightly
curved.
Further, the fins 60 are arranged in a plurality of parallel rows
substantially along
the whole length of the tubing element 10.
The fins 60 and the connection walls 45, 55 are arranged such to each other
that
they enclose an angle y.
However, this angle y may be substantially perpendicular. Alternatively, this
angle
y may be chosen within range of about 15 to about 60 and may be preferably
chosen within a range of about 20 to about 25 . An angle y of about 45
between the fins 60 at least one of the connection walls 45, 55 is considered
to
be substantially neutral, in particular as a neutral arrangement with respect
to
the interference with e.g. fans or the like, which are connected or used
together
with a heat exchanger means comprising such a tubing element 10.
The fins 60 are formed slightly concave or convex, which is, however, not
mandatory. In particular, the slightly concave or convex shape of the fins 60
may
be achieved by an offset of the center part of the middle section of the fins
60
with respect to the endpoints of the fins 60 within a range of about 0.5 mm to
about 5 mm, preferably of about 1 mm to about 2 mm, most preferred of about
1.5 mm. In the embodiment shown in Figure 2, the offset of the center part of
the middle section of the fins 60 with respect to the endpoints of the fins 60
is
about 1 mm.
The fins 60 are arranged such that the medium flowing against the fins flows
against a concave formed part of the fin.
Furthermore, the fins 60 according to the embodiment shown in Figure 2 have a
height of about 2.5 mm. Generally, the fins 60 may have a height chosen within
a
range of about 0.5 mm to about 5.0 mm, preferably about 2-3 mm.
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At the ends 20, 30 of the tubing element 10 collecting elements 25, 35 are
provided, which reduce width of the tubing element 10 to a broader diameter,
i.e.
the diameter of the tubular connectors of circular cross-sections 27, 37.
Figure 7 is a perspective view of a heat exchanger means 100 comprising a
plurality of a first set of interlaced tilted helical microchannel tubing
elements 10
with adjacent tilted and twisted similarly helically formed tubing elements 10
and
a respective second set 52 inside of the first set Si. By this, a compact
structure
together with an increased surface for heat exchange is received.
Figure 8 is a perspective view of the second embodiment of the tubing element
according to the present invention. The second embodiment of the tubing
element 10' is merely the same as the one shown in Figures 2 to 6. However, a
different kind of fins is used, i.e. fins 60'. The fins 60' are arranged along
a curve
extending substantially the whole width W of at least one of the outer
surfaces
42, 52 of the sidewall 40 and sidewall 50 and as can be seen from Figure 9,
between each fins 60' arranged along one curve a gap is provided. The fins 60'
are arranged in a plurality of rows which are arranged parallel.
The fins 60' are according to the embodiment shown in Figure 8 arranged on an
angle of 22.5 degrees to the outer surfaces 42, 52 of the first side wall 40
and of
the second side wall 50.
Alternatively, the fins 60' may be inclined arranged on at least one of the
outer
surfaces 42, 52 of the first side wall 40 and/or of the second side wall 50,
whereby exemplarily the angle between the fins 60' and the outer surface 40,
50
is substantially perpendicular.
Furthermore, the fins 60' are arranged along a curve extending along the whole
width W of the outer surfaces 42, 52 of the first side wall 40 and/or of the
second side wall 50 and are also curved, whereby between the fins 60' being
arranged along a curve is a gap 62.
It is possible that the fins 60' and the curve of fins 60' and the connection
walls
45, 55 are arranged such to each other that they enclose an angle y.
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However, this angle y may be substantially perpendicular. Alternatively, this
angle
y may be chosen within range of about 15 to about 600 and may be preferably
chosen within a range of about 200 to about 25 . An angle y of about 450
between the fins 60 at least one of the connection walls 45, 55 is considered
to
be substantially neutral, in particular as a neutral arrangement with respect
to
the interference with e.g. fans or the like, which may be connected or used
together with a heat exchanger means comprising such a tubing element 10.
The fins 60' and the curve of fins 60' is formed slightly concave. In
particular, the
slightly concave shape of the fins 60' is achieved by an offset of the center
part
of the middle section of the fins 60' and the curve of fins 60' with respect
to the
endpoints of the fins 60' and the curve of fins 60' within a range of about
0.5 mm
to about 5 mm, preferably of about 1 mm to about 2 mm, most preferred of
about 1.5 mm.
The fins 60' are arranged such that the medium flowing against the fins 60'
flows
against a concave formed part of the fins 60'.
Furthermore, the fins 60' according to the embodiment shown in Figure 8 have a
height of about 3 mm. Generally, the fins 60' may have a height chosen within
a
range of about 0.5 mm to about 5.0 mm, preferably about 2-3 mm.
The curves of fins 60' are arranged in a plurality of substantially parallel
rows
along the tubing element.
Figure 9 is showing in detail embodiment of a tube 10' with fins 60' as shown
in
Figure 8 and having a plurality of microchannels 70 with a square cross-
section.
Figure 10a shows in a perspective view a draining plate 80 which is tilted and
helically wound such that it can be attached to the helically wound heat
exchanger microchannel tube 10 as shown in Figure 10b.
As can be further seen from Figure 11, several draining plates 80 and heat
exchanger tubes 10 may be arranged to a heat exchanger means 100 comprising
a plurality of interlaced sloped and tilted helically wound microchannel
tubing
elements 10 and draining plates 80 between each of the pair of adjacent tubing
elements 10.
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The use of draining plates 80 is preferred in cases where the heat exchanger
means 100 is an evaporator.
