Field of invention
[0001] The invention relates to a heat exchanger comprising a stack of heat exchanger plates
stacked one on top of the other along a stacking direction.
Technical Background
[0002] Plate heat exchangers for transferring heat between different mediums, e.g., different
fluids or gases, are well known in the art. The plate heat exchanger may comprise
a stack of a plurality of heat exchanger plates stacked one on top of the other between
two end plates. A first set of channels may be formed in every second interspace between
the heat exchanger plates and a second set of channels may be formed in the other
interspaces between the heat exchanger plates. The components of the plate heat exchangers
and especially the heat exchanger plates are typically made of metal but could be
made of any other material as long as it is sufficiently strong and has sufficient
heat conduction properties. The components of the plate heat exchange may be assembled
by being clamped between the end plates, or by using brazing, bonding, or welding
by way of example. Since the mediums are in contact with a large surface area on a
respective side of each heat exchanger plate a plate heat exchanger provides an efficient
heat transfer. Plate heat exchangers may be of a kind often referred to as plate-fin
heat exchanger. A plate-fin heat exchanger typically comprises a stack of heat exchanger
plates with wave-shaped structures sandwiched between the heat exchanger plates.
[0003] In order to make efficient use of the available surface area of the heat exchanger
plates, it is typically desirous to design the heat exchanger such that is displays
an efficient distribution, and typically also an efficient collection, of the flow
of medium across the whole width of the heat exchanger plates. Further, it is typically
desirous to design the heat exchanger such that it is mechanically stable in relation
to material consumption, manufacturing costs and/or final weight.
[0004] In an attempt to address this, document
CN 207963578 U discloses a plate and fin heat exchanger with guiding distribution fins and exchanging
fins.
[0005] However, as will be explained below, the prior art document does not disclose a heat
exchanger which adequately addresses the set of design criteria of providing an efficient
distribution, and preferably also an efficient collection, of the flow of medium across
the whole width of the heat exchanger plates, while preferably also considering that
the heat exchanger should be mechanically stable in relation to material consumption,
manufacturing costs and/or final weight.
Summary of invention
[0006] It is an object of the invention to provide a heat exchanger which adequately addresses
the set of design criteria of providing an efficient distribution, and preferably
also an efficient collection, of the flow of medium across the whole width of the
heat exchanger plates, while preferably also considering that the heat exchanger should
be mechanically stable in relation to material consumption, manufacturing costs and/or
final weight.
[0007] This object has been achieved by a heat exchanger comprising a stack of heat exchanger
plates stacked one on top of the other along a stacking direction,
a first set of channels formed in every first second interspace between the heat exchanger
plates,
a second set of channels formed in every second second interspace between the heat
exchanger plates,
wherein, in each of the channels in the first and second set of channels fin structures
formed of sheets being folded back and forth are positioned between the heat exchanger
plates such that the respective fin structure abuts the heat exchanger plates along
a plurality of contact lines having a main extension extending in parallel with a
longitudinally extending fin direction thereby defining plurality of fluid channels
forming said first and second set of channels,
wherein each heat exchanger plate comprises four through-going openings formed at
a respective corner portion of the respective heat exchanger plate and configured
to form a first inlet port extending through the stack along the stacking direction,
a first outlet port extending through the stack along the stacking direction, a second
inlet port extending through the stack along the stacking direction, and a second
outlet port extending through the stack along the stacking direction, the first inlet
port and first outlet port being in fluid connection with each other via the first
set of channels and the second inlet port and second outlet port being in fluid connection
with each other via the second set of channels,
wherein the heat exchanger further comprises, in each interspace between the heat
exchanger plates, a distribution structure at the respective inlet port and a collection
structure at the respective outlet port,
wherein the respective distribution structure, respectively the respective collection
structure is positioned between the respective port and the respective fin structure
in the respective first and second set of channels,
wherein an internal interface between the respective distribution structure and the
fin structure and/or an internal interface between the respective collection structure
and the fin structure in the respective channel of the first set of channels and/or
in the respective channel of the second set of channels is inclined relative to the
longitudinally extending fin direction and is inclined also relative to a transversal
direction.
[0008] The first and second set of channels are alternatingly arranged such that there in
every interspace between the heat exchanger plates is either a channel of the first
set of channels or a channel of the second set of channels. This may also be expressed
as that the first and second set of channels are alternatingly arranged such that
there is a channel of the first set of channels in every second interspace and that
there is a channel of the second set of channels in the other interspaces between
the heat exchanger plates, i.e., in the interspaces not forming part of the first
set of channels. In the phrase "every first second interspace", the word "first" is
mainly a label within the phrase "every second interspace". In the phrase "every second
second interspace", the first instance of the word "second" is mainly a label within
the phrase "every second interspace". It may be noted that it is conceivable that
the repeating pattern of either a channel of the first set of channels or a channel
of the second set of channels in every interspace between the heat exchanger plates
may after a plurality of repetitions be interrupted. Similarly, the ports extending
through the stack may extend through all the plates of the heat exchanger or may extend
through only a sub-set of neighbouring plates forming one stack. This latter configuration
may e.g., be the case where there is a plurality of stacks brought together to form
a combined heat exchanger. One example where such different configurations may be
used is e.g., in a so-called multi-pass heat exchanger.
[0009] It may be noted that in a preferred embodiment, the fin structure/-s is/are folded
such that every fold has an extension sufficient to bridge the distance between neighbouring
heat exchanger plates such that the respective fin structure abuts the neighbouring
heat exchanger plates between which it is positioned. In a preferred embodiment, the
respective fin structure abuts the respective heat exchanger plate along a plurality
of contact lines extending along the longitudinally extending fin direction, with
the actual abutment forming continuous or semi-continuous line contacts. It may in
this context be noted that the fin structure may be folded along straight lines such
that the contact lines may be straight lines extending along the longitudinally extending
fin direction. The fin structure may however be folded along lines having other shapes,
such as e.g., wavy or curved lines such that the contact lines become wavy or curved
lines undulating back and forth along a main extension. Irrespective of the shape
of the fold lines, it is preferred that the main extension extends in parallel with
a longitudinally extending fin direction.
[0010] In a preferred embodiment, the channels in the first set of channels, preferably
each of the channels in the first set of channels, comprises a respective first fin
structure positioned between the heat exchanger plates, and the channels in the second
set of channels, preferably each of the channels in the second set of channels, comprises
a respective second fin structure positioned between the heat exchanger plates. However,
it should be noted that it is also conceivable that the heat exchanger may be designed
such that only the channels in the first set of channels comprises fin structures.
Alternatively, it is also conceivable that the heat exchanger may be designed such
that only the channels in the first set of channels comprises fin structures.
[0011] The stacking direction is preferably orthogonal to the longitudinally extending fin
direction.
[0012] The fin structure may be said to form part of a heat transfer area at which heat
is transferred to or from the respective medium from or to the respective heat exchanger
plate. Since the respective fin structure is formed such that it presents a plurality
of folds, or interspaced walls, bridging the height of the respective channel, the
medium in the respective channel is in contact with not only the respective heat exchanger
plate but also all the folds or interspaced walls in said channel. Since the respective
fin structure also abuts the heat exchanger plates, the heat may be transferred from
the medium directly to the respective heat exchanger plate and also indirectly by
being transferred to the fin structure which in turn transfers it to the respective
heat exchanger plate.
[0013] The fin structure may be in the form of a thin sheet being folded back and forth.
The fin structure is preferably formed of a thin metal sheet being folded back and
forth. This may be referred as that the fin structure is folded back and forth in
an accordion-like design. The folds back and forth may have different designs. The
folds may e.g., be shaped as a repeating triangular wave, a repeating square wave,
a repeating sinus wave, or combinations thereof. The folds may e.g., be a repeating
square wave with a fully rounded top/bottom or rounded corners on each side of the
top/bottom at of each period. The rounding may e.g., be in the shape of a sinus wave
or a radius. The folds may be in the form of an undulating pattern, which also may
be referred to as a repeating pattern of interconnected U:s and inverted U:s.
[0014] An advantage with folds based on a square wave, sinus wave or undulating pattern
is that the area of the fin structure that abuts the heat exchanger plates is increased
compared to e.g., a folding pattern formed of repeating triangular waves. When this
abutment area is increased, an increased heat transfer may be achieved. In any case,
the fact that the fin structure abuts the heat exchanger plates, provides for an improved
stability between the fin structure and the heat exchanger plates. This is further
advantageous as it allows for a mechanically stable heat exchanger with improved structural
support.
[0015] The respective fin structure is positioned, as seen along the flow direction of the
respective medium, between the respective distribution structure and the respective
collection structure. As mentioned above, the respective distribution structure is
positioned between the respective inlet port and the respective fin structure in the
respective first and second set of channels. The respective distribution structure
is configured to distribute a flow from the respective inlet port to the respective
fin structure such that the flow of medium is distributed over the whole width of
the respective channel. The respective collection structure is configured to collect
the flow from the respective fin structure and to direct the flow to the respective
outlet port.
[0016] By designing the internal interface between the respective distribution structure
and the fin structure and/or an internal interface between the respective collection
structure and the fin structure in the respective channel of the first set of channels
and/or in the respective channel of the second set of channels such that it is inclined
relative to the longitudinally extending fin direction and inclined also relative
to a transversal direction, it is facilitated to design the heat exchanger with different
shapes and sizes of the ports and still make use of distribution and/or collection
structures formed of fin structures formed of a material being folded back and forth.
Such a distribution or collection fin structure has a plurality of channels extending
along its own or local fin direction and it has to have one edge extending along that
local fin direction and one side forming the interface to the port, and one side forming
the interface with the main fin structure. By allowing the interface between the distribution
or collection structure and the main fin structure to be inclined, it opens up for
a greater variation of the shape of the interface with the port and still allowing
the distribution or collection structure to be basically triangular or truncated triangular
shaped which in turn facilitates manufacture and assembly.
[0017] The respective internal interface may form an angle β with the fin direction, wherein
the angle β is between 95 and 130°, preferably between 95 and 120°, or between 50
and 85°, preferably between 60 and 85°.
[0018] It may in this context be noted that the angle β may be angled such that there are
two options available for the designer to use depending upon e.g., the desired relative
shapes and sizes of the ports at the same transversally extending side, i.e., of the
ports at the same longitudinal position, the desired thickness of the pressed panel
portions closing of the ports, the desire size and shape of the ports in relation
to the transversal width of the heat exchanger.
[0019] It may also be noted that the internal interface may in some cases, see e.g., figure
6, be inclined in the same direction on both major surfaces at the same ports. For
instance, if there is a significant difference in the sizes of the ports with one
large port and one small port arranged side by side, the internal interface is typically
inclined such that it is closer to a transversally extending midline of the heat exchanger
at the longitudinal side closest to the large port on both major surfaces of the heat
exchanger plate and further away from said transversally extending midline of the
heat exchanger at the longitudinal side closest to the small port on both major surfaces
of the heat exchanger plate. The angle β on one of the major surface may however be
sligtly different from the angle β on the other major surface since the area available
is basically determined by the port size and the pressed portion selectively closing
of one or the other port. In figure 6, the large port to the left is open to the channel
in front of the plate whereas the small port to the right is closed off from the channel
in front of the plate. On the other side, the general direction of inclination is
the same but since there is a pressed portion along the underside of the large port
to the left, right if viewed from the opposite side, closing it off from the channel
on the other side of the plate wherby the left hand side, right hand side if viewed
from the opposite side, of the interface need to be slightly lower than in figure
6 whereas to the right hand side, left hand side if viewed from the opposite side,
the interface may extend all the way up to the lower corner of the smaller port since
that port is open to the channel on the other side of the plate. Thus, the inclination
is slightly larger on the other side of the plate where the larger port is closed
off from the channel on that side of the plate.
[0020] It may also be noted that the internal interface may in some cases, see e.g., figure
7, be inclined in opposite directions on the two major surfaces at the same ports.
For instance, if there is no significant difference in the sizes of the ports, the
internal interface is typically inclined such that it on a first major side is closer
to a transversally extending midline of the heat exchanger at the longitudinal side
closest to the port being closed off from the channel on that major surface and further
away from said transversally extending midline at the longitudinal side closest to
the port being open to the channel on that major surface. Since the ports are of the
same or about the same size, the available area is varied mostly by the presence or
absence of the pressed portion closing off said port from the channel at the respective
major surface. The angle β on one of the major surface may be the same or be sligtly
different from the angle β on the other major surface since the area available is
basically determined by the port size and the pressed portion selectively closing
of one or the other port. In figure 7, the port to the left is open to the channel
in front of the plate whereas the port to the right is closed off from the channel
in front of the plate. On the other side of the plate, the general direction of inclination
of the internal interface is opposite since there is a pressed portion along the underside
of the port to the left, to the right if viewed from the other side, whereas to the
right hand side, left hand side if viewed from the other side, the interface may extend
all the way up to the lower corner of the right hand port, left hand port if viewed
from the opposite side, since that port is open to the channel on the other side of
the plate. Thus, the inclination is bascially opposite on the other side of the plate.
It may also be noted that one of the interfaces may be angled an angle β between 95
and 130°, preferably between 95 and 120°, or between 50 and 85°, preferably between
60 and 85°, whereas the interface directly opposite on the other major side of the
plate may be angled 90° to the fin direction. It may also be noted that it is conceivable
that both interfaces on both major sides of a plate are angled 90° to the fin direction.
Similarly, it may also be noted that one of the interfaces, such as the interface
at the distribution structure or the collection structure may be angled an angle β
between 95 and 130°, preferably between 95 and 120°, or between 50 and 85°, preferably
between 60 and 85°, whereas the interface at the other one of the distribution structure
or the collection structure may be angled 90° to the fin direction. It may also be
noted that it is conceivable that both interfaces at both the distribution structure
and the collection structure are angled 90° to the fin direction. Thus, there are
for each plate four internal interfaces that may be selected to be angled differently.
[0021] The respective internal interface may extend along a substantially straight line.
This is advantageous since it facilitates production of the distribution and/or collection
structure and of the fin structure while still allowing for different designs of the
ports and while still allowing for a smooth distribution of the flow of medium across
the width of the heat exchanger. It is preferred that the straight line is straight
in the sense that along at least a central portion forming 75% of its length, any
deviation transverse to its extension is less than +-10% of its length.
[0022] The internal interface at the respective inlet port and the internal interface at
the respective outlet port are preferably inclined in the same general direction relative
to the transverse direction.
[0023] Thus, the internal interface at the first inlet port and the internal interface at
the first outlet port is preferably inclined in the same general direction, a first
direction, relative to the transverse direction. Furthermore, the internal interface
at the second inlet port and the internal interface at the second outlet port are
preferably inclined in the same general direction, a second direction, relative to
the transverse direction. However, as mentioned above, the general direction of inclination
on the opposite major surfaces may be the same or may be opposite. Thus, the first
general direction may be the same as or be opposite to the second direction. Being
inclined in the same general direction may be said as that both directions are within
an angular range being less 90° or that both directions are within an angular range
being greater than 90° relative to the fin direction. Being inclined in opposite general
directions may be said as that one of the directions is within an angular range being
less 90° and that the other direction is within an angular range being greater than
90°.Thus, the phrase the internal interface at the respective inlet port and the internal
interface at the respective outlet port are preferably inclined in the same general
direction relative to the transverse direction is intended to refer to the fact that
the respective internal interface of the first set of channels has the same general
direction at the first inlet ports as the internal interface of the first set of channels
has at the first outlet ports. Similarly, the respective internal interface of the
second set of channels has the same general direction at the second inlet ports as
the internal interface of the second set of channels has at the second outlet ports.
It may in this context also be noted that the interfaces are only said to be inclined
in the same general direction relative to the transverse direction, i.e., they are
not necessarily at the same angle β, but only that both have an angle being greater
than 90° or both have an angle being less than 90° relative to the fin direction.
However, preferably the internal interface close to the first inlet port is inclined
an angle β being the same as the angle β of the inclination of the internal interface
close to the first outlet port. Similarily, the internal interface close to the second
inlet port is inclined an angle β being the same as the angle β of the inclination
of the internal interface close to the second outlet port. However, as discussed in
detail above, the angle β on the first major side may or may not be the same as the
angle β on the other major side, e.g., dependeing upon if the ports are of significalty
different size or if they are of the same or about the same size.
[0024] A port interface between the respective inlet port and the respective distribution
structure, respectively a port interface between the respective outlet port and the
collection structure may be inclined relative to the fin direction such that a distance
between the port interface and the fin structure, as measured along the fin direction,
increases with increasing distance, as seen along a line extending across the fin
direction, from an edge of the respective heat exchanger plate which is closest to
the respective port and which extends along the longitudinally extending fin direction.
[0025] The respective fin structure is positioned, as seen along the flow direction of the
respective medium, between a respective distribution structure and a respective collection
structure. As mentioned above, the respective distribution structure is positioned
between the respective inlet port and the respective fin structure in the respective
first and second set of channels. The respective distribution structure is configured
to distribute a flow from the respective inlet port to the respective fin structure
such that the flow of medium is distributed over the whole width of the respective
channel. The respective collection structure is configured to collect the flow from
the respective fin structure and to direct the flow to the respective outlet port.
[0026] The disclosed design is advantageous as it allows for an improved distribution of
the medium in the first set of channels. The disclosed design is further advantageous
as it allows for an improved distribution of the medium in the second set of channels.
The disclosed design is advantageous as it allows for an improved collection of the
medium in the first set of channels. The disclosed design is further advantageous
as it allows for an improved collection of the medium in the second set of channels.
[0027] By the port interface between the respective inlet port and the respective distribution
structure being inclined relative to the fin direction it is facilitated to provide
an optimized flow such that the distribution of the medium in the first and/or second
set of channels is improved. The inclined port interface allows for a large interface
between the respective inlet port and the respective distribution structure. The inclined
port interface allows for the inlet port to be designed in a skewed or basically triangular,
or at least partly triangular, shape such the interface is comparably large in relation
to the ports total surface area. The inclined port interface also allows for the provision
of a large interface of the distribution structure in a simple and cost-efficient
manner. It is e.g., possible to manufacture the distribution structure from a basically
triangular or truncated triangular sheet being folded back and forth in a manner similar
to the fin structure discussed above. Thus, the inclined port interface facilitates
the provision of the flow being distributed over the whole width of the distribution
structure thereby in turn facilitating the provision an optimized the flow over the
width of the heat exchanger.
[0028] By the interface between the respective outlet port and the respective collection
structure being inclined relative to the fins structure it is facilitated to accomplish
an efficient collection of the medium in the first or second set of channels and thereby
in turn it is facilitated to accomplish an optimisation of the flow over the width
of the heat exchanger. The advantages discussed above in relation to the inclined
port interface between the inlet port and the distribution structure is correspondingly
applicable for the inclined port interface between the respective outlet port and
the respective collection structure.
[0029] The respective port interface may form an angle α with the fin direction. As mentioned
above, the interface is inclined relative to the fin direction, i.e., the angle α
is greater than 90°, but smaller than 180°, such that the respective interface is
inclined. Greater than and smaller than may in this context refer to at least 5° from
90° respectively 180°. The angle α is measured between on the one hand a line being
centrally positioned as seen in the transverse direction and extending along the fin
direction and on the other hand the side of the interface facing the distribution
or collection structure. Preferably the angle α is between 110 and 160°, more preferably
between 120 and 150°. This is advantageous as it allows for optimizing the flow such
that the distribution of medium and/or the collection of medium as discussed above
is improved. It may be noted that the port interface of the distribution structure
may, but need not, be inclined the same angle as the port interface of the collection
structure.
[0030] The respective port interface may extend along a substantially straight line. This
is advantageous as it allows for a good distribution of the medium from the respective
inlet port to the fin structure. This is advantageous as it allows for a good collection
of the medium from the fin structure. This is further advantageous as it allows for
fatigue optimizing in the heat exchanger. It is preferred that the straight line is
straight in the sense that along at least a central portion forming 75% of its length,
any deviation transverse to its extension is less than +-10% of its length.
[0031] The respective distribution structure, and/or the respective collection structure,
extends from a first, transversally central, corner of the respective port towards
a second, transversally outer, corner of the respective port and leaves a transversally
extending gap at the longitudinally extending edge being closest to the respective
port.
[0032] The term "transversally central" in the phrase "a first, transversally central, corner"
refers to that the first corner is positioned centrally as seen along the transverse
direction. Correspondingly, "the second, transversally outer, corner" refers to a
corner which is positioned closer to an outer portion as seen along the transverse
direction compared to the position of the first corner.
[0033] It may be noted that in a preferred embodiment, the first corner is positioned at
a distance from the second corner both in the fin direction and in the transversal
direction such that the port interface between the respective inlet port and the respective
distribution structure is inclined. It may be noted that in a preferred embodiment,
the first corner is positioned at a distance from the second corner both in the fin
direction and in the transversal direction such that the port interface between the
respective outlet port and the respective collection structure is inclined.
[0034] The gap may with reference to the preferred embodiments with the inclined port interface
also be expressed as that there is a corner piece of the respective distribution structure,
and/or the respective collection structure missing.
[0035] Providing a gap is e.g., advantages when it comes to manufacture of the respective
distribution structure, and/or the respective collection structure. By allowing a
gap to be formed it is e.g., possible to allow a respective distribution structure,
and/or a respective collection structure being inclined and still ending as seen along
the transversal direction in an end portion being formed of a piece of material having
an extension along the fin direction also at the transversal outer perimeter which
makes such an end portion significantly stronger compared to if the respective distribution
structure, and/or the respective collection structure would end in a sharp corner.
[0036] An open gap may also aid in distributing the flow over a couple of the transversally
outermost channels thereby reducing the risk that turbulence or other corner effects
in the flow from the ports to the channels in the fin structure results in any undesired
imbalances in the flow in the channels closest to the longitudinal edge.
[0037] The gap preferably has a transversal extension being at least equal to three channels
formed of the folds of the fin shaped structure of the respective distribution structure,
and/or the respective collection structure.
[0038] A major portion of a flow from the respective inlet port is preferably distributed
via the distribution structure to the fin structure, respectively a major portion
of a flow from the fin structure is preferably collected via the collection structure
to the respective outlet port; and
wherein a minor portion of the flow from the respective inlet port may be transferred
to the fin structure via said gap, respectively a minor portion of the flow from the
fin structure may be transferred to the respective outlet port via said gap.
[0039] This is advantageous as it allows to distribute the flow along the entire width of
each heat exchanger plate seen along the transversal direction, wherein the major
portion of the flow is distributed via the distribution structure and the minor portion
of the flow is distributed to the fin structure via the gap. This is further advantageous
as it allows to collect the flow from the entire width of each heat exchanger plate
seen along the transversal direction, wherein the major portion of the flow is collected
via the collection structure and the minor portion of the flow is collected from the
fin structure via the gap. The disclosed design, in which the gap is introduced, is
advantageous as it allows for an improved and efficient flow distribution and flow
collection along the entire width of the heat exchanger plate. Preferably at least
80%, more preferably at least 90%, of the flow is distributed and/or collected via
the respective distribution structure, and/or the respective collection structure.
[0040] A cut in the respective plate forming the respective port may be arc-shaped along
at least a major portion of a transversal extension of said gap. The arc-shaped design
of the respective port in the gap may facilitate provision of smoothly directing the
minor portion of the flow into the fin structure without the need of being distributed
via the distribution structure. This helps to improve the flow distribution throughout
the fin structure hence the flow distribution is optimized. The design of the respective
port and the distribution structure may cooperate in order to direct and distribute
the medium to the fin structure in an efficient way. The arc-shaped design of the
respective port in the gap may further facilitate provision of smoothly collecting
the minor portion of the flow from the fin structure without the need of being collected
via the collection structure. The design of the respective port and the collection
structure may cooperate in order to direct and collect the medium from the fin structure
in an efficient way. Moreover, an arc-shaped portion of this kind will result in reduced
local mechanical stress which is especially beneficial when it comes to the plates
possibility to withstand fatigue.
[0041] The distribution structure may be formed by a basically triangular or truncated triangular
fin structure. The shape is basically triangular or truncated triangular with the
normal of the triangle surface extending in the stacking direction. It may be noted
that in a preferred embodiment, the fin structure of the distribution structure, i.e.,
the folds back and forth, may have a similar structure as the fin structure discussed
above. In that case, the distribution structure typically has diagonally extending
fins; diagonally relative to the fin direction. This is advantageous as it allows
to distribute the flow from a port positioned in a corner of the plate over the whole
transversal width and still allowing the respective distribution structure, and/or
the respective collection structure to be manufactured by folding a sheet of material
back and forth. The fin structure of the respective distribution structure, and/or
the respective collection structure aids in keeping the heat exchanger plates at their
intended mutual distances as seen along the stacking direction. The multiple contact
lines formed by the fin structure at the respective distribution structure, and/or
the respective collection structure also takes part in the provision of a heat transfer.
It may be noted that in a preferred embodiment, the fin structure of the respective
distribution structure, and/or the respective collection structure has vertical fins
or folds as seen along the fin direction.
[0042] The collection structure may be formed by a basically triangular or truncated triangular
fin structure. The shape is basically triangular or truncated triangular with the
normal of the triangle surface extending in the stacking direction. It may be noted
that in a preferred embodiment, the fin structure of the collection structure, i.e.,
the folds back and forth may have a similar structure as the fin structure discussed
above. In that case, the collection structure typically has diagonally extending fins
as seen relative to the fin direction. The advantages have been discussed above with
reference to the corresponding structure of the respective distribution structure.
[0043] The respective ports may be formed as substantially triangular ports. The respective
triangular inlet port helps to match the respective triangular distribution area in
an easy and efficient way. The respective triangular outlet port helps to match the
respective triangular collection area in an easy and efficient way.
[0044] The dimensions of the first inlet and outlet ports may be different from the dimensions
of the second inlet and outlet ports.
[0045] In this context, the term "dimensions" should be interpreted as a total area of the
first ports being different from a total area of the second ports. The first ports
and the second ports are in one preferred embodiment asymmetric in relation to each
other. This allows for a difference in total flow of the first medium in relation
to total flow of the second medium.
[0046] However, it may also be noted that in other preferred embodiments, the first ports
and the second ports have the same size and shape. This is typically the case if the
total flow of the first medium is intended to be about the same as the total flow
of the second medium.
[0047] It may be noted that it is also conceivable to have asymmetry in dimension in the
inlet ports for one medium in relation to the outlet ports for the same medium. This
allows for an efficient flow of said medium even in cases the medium undergoes significant
changes in properties as it flows through the heat exchanger. Such a change could
for instance involve a phase change of all or parts of the medium between a liquid
and a gaseous phase.
[0048] The first inlet port may be arranged on a first longitudinally extending side of
the stack of heat exchanger plates and the first outlet port may be arranged on a
second longitudinally extending side of the stack of heat exchanger plates, the second
longitudinally extending side being opposite the first longitudinally extending side.
[0049] The second inlet port may be arranged on the first longitudinally extending side
of the stack of heat exchanger plates and the second outlet port may be arranged on
the second longitudinally extending side of the stack of heat exchanger plates, the
first longitudinally extending side being opposite the second longitudinally extending
side.
[0050] Opposite refers in this context to opposite the transversal direction. With this
arrangement, a diagonally extending flow path between the first inlet and outlet and
preferably also between the second inlet and outlet is formed. With the disclosed
design, it is facilitated to provide an improved distribution and collection of the
medium in the heat exchanger. The provision of a diagonally extending flow may provide
a good heat transfer.
[0051] In an alternative embodiment, the inlet ports and the outlet ports of the first medium
are both arranged on the first longitudinally extending side of the stack of heat
exchanger plates and the inlet ports and the outlet ports of the second medium are
both arranged on the second longitudinally extending side of the stack of heat exchanger
plates, the second longitudinally extending side being opposite the first longitudinally
extending side.
[0052] In accordance with one embodiment, the inlet port of the first medium is positioned
at the same transversally extending side as the outlet port of the second medium and
outlet port of the first medium is positioned at the same transversally extending
side as the inlet port of the second medium. Thereby the two mediums flow in opposite
directions as seen along the longitudinally extending fin direction. This may be referred
to as a counter-flow. Alternatively, the inlet ports of both mediums are positioned
at the same transversally extending side and the outlet ports of the mediums are positioned
at the other transversally extending. This may be referred to as a parallel flow.
Both the counter-flow and the parallel flow may be combined with both the diagonal
flow or with the flow with both the inlet ports and the outlet ports of the first
medium are both arranged on the first longitudinally extending side of the stack.
It may in this context also be noted that it is conceivable that the heat exchanger
is designed such that it allows the flow direction to be changed for one or both of
the mediums between different operational states. It is e.g., conceivable that the
first medium flows in a first flow direction in a first operational state in the opposite
direction in a second operational state. In such a case the port referred to the inlet
port will become the outlet port and vice versa. Similarly, the structure referred
to as the distribution structure will become a collection structure and vice versa.
[0053] Each fin structure of each of the channels of the first and second set of channels
may comprise at least a first and a second part arranged one after the other along
the fin direction. Normally, there are manufacturability constraints on the maximum
length of the fin structure along the flow direction. Such manufacturability constraints
are e.g., introduced by the fact that there are difficulties to in a cost-efficient
manner manufacture and transport sheet metal on sheet metal rolls over a certain width.
It is also often difficult to in a cost-efficient manner fold the sheets back and
forth if they are larger than a certain width. A common maximum fin length is 500
mm. In order to manufacture heat exchangers of dimensions having channels longer than
this, several fin structures need to be arranged in series on after the other along
the flow direction. Therefore, an advantage with this design is that the heat exchanger
may be provided with longer channels without being restricted by the manufacturability
constraints.
[0054] The interface between the first and second part of each of the fin structures will
be defined by a transversally extending edge of the first part being opposite to and
facing a transversally extending edge of the second part. In some embodiments the
transversally extending sides of the first and second part being opposite to each
other may abut each other. In some embodiments the transversally extending sides of
the first and second part being opposite to each other may be separated from each
other by a gap. The interface between the first and second part of the first fin structure
is positioned at a first position along the fin direction. If there is a gap present,
the position is defined as the mid-point of the gap. The interface between the first
and second part of the second fin structure is positioned at a second position along
the fin direction. The first position respectively the second position is determined
by choosing the dimensions of the first and second part in each of the fin structures.
In order to facilitate assembly, the dimensions, or at least the tolerances, of the
first and second part are typically chosen such that the actual total length is slightly
shorter than the nominal space available. This often results in that a small longitudinal
gap is formed between the first and second parts. It may in this context be noted
that such a gap may also be deliberately provided. Independently of if the gap is
unwanted but an unavoidable or deliberately provided for, it is advantageous to choose
the dimensions of the first and second parts of the first fin structure in relation
to the dimensions of the first and second parts of the second fin structure such that
the interface between the first and second parts of the first fin structure becomes
separated a longitudinal distance from the interface between the first and second
parts of the second fin structure. With such a design it is secured that the any gap
between the first and second parts of the first fin structure does not fully align
with any interface between the first and second parts of the second fin structure.
That is, it is secured that any gap on a first side of a heat exchanger plate does
not fully align with any gap on a second side of the same heat exchanger plate.
[0055] It has been found that if there are gaps on both sides of a heat exchanger plate,
there is a risk that the heat exchanger plate becomes deformed. Such deformation may
occur during the manufacture or during use.
[0056] By the interfaces of the first and second fin structure being positioned at a first
position and a second position, respectively, and which are being separated a longitudinal
distance from each other, the heat exchanger plates will be subject to minimal amount
of deformation. Deformation of the heat exchanger plates affects the flow of the medium
through the channel in that there is a risk that the flow in each of the channels
will be inconsistent and not optimized. In worst case, deformation might be so acute
that the flow may risk being completely disrupted in some channels. Deformation of
the plates may also give rise to turbulence in the flow past or after the deformation.
Thus, deformation of the channels may result in the heat exchanger not functioning
efficiently. The disclosed design is advantageous in that it facilitates the provision
of channels that are mechanically strong and resistant to deformation, hence allowing
for an optimized flow such that the intended efficiency of the heat exchanger is achieved.
The disclosed design is also advantageous in that allows for large heat exchangers
being manufactured in a cost-efficient manner. It may in this context also be noted
that the gap may be formed of parallel edges of the first and the second part, or
that the gap may be formed of the edges of the first and second part being angled
relative to each other and thereby forming a triangular shape, or a trapezoid shape
with the parallel sides formed of the longitudinal sides of the plates. It may also
be noted that the gap may be formed as a void or lack or material through-out the
complete width of the plates or alternatively that the gap may be formed by one or
both of the parts having a plurality of protrusions forming intermittent abutments
and a non-continuous gap between the parts of the fin structure. The protrusions may
be formed as rods, small rectangular pieces, or the like. Alternatively, the protrusions
may be formed by cutting the edge/edges of the part/parts in a non-straight manner,
such as e.g., in a saw tooth pattern, a wave-shaped pattern, such as a sinus wave
or square wave pattern, such that the ridges of the tooths or waves of one part abuts
the edge of the other part. Intermittent abutments may be used to provide a controlled
size of any gap.
[0057] The dimensions of the first and second parts of the first and second fin structure
is preferably chosen such that the distance between the first and second positions
is such that any longitudinal gap at the central interface between the first and second
part in the first channel of the first set of channels at least does not overlap a
midline of any longitudinal gap at the central interface between the first and second
part in the first channel of the second set of channels, and vice versa. This may
shortly also be referred to as that any gap between the first and second part in the
first channel of the first set of channels does not exceed a midline of any gap between
the first and second part in the first channel of the second set of channels, or vice
versa.
[0058] This is advantageous as it provides channels which are mechanically strong and resistant
to deformation which allows for optimizing the flow in the channels such that the
efficiency of the heat exchanger is improved.
[0059] It has been found that there is an improvement in the strength of the heat exchanger
in case any overlap of the gaps is limited such that a gap does not exceed a midline
of any gap on the opposing side of the same heat exchanger plate. Midline refers to
an imaginary line or position positioned at equal distance to the respective edges
of the first and second part facing each other as measured along the fin direction.
Exceed refers to the extension of the gap along the fin direction.
[0060] The dimensions of the first and second parts of the first and second fin structure
is preferably chosen such that the distance between the first and second positions
is such that any longitudinal gap at the central interface between the first and second
part in the first channel of the first set of channels does not overlap with any longitudinal
gap at the central interface between the first and second part in the first channel
of the second set of channels, and vice versa.
[0061] It has been found that there is an improvement in the strength of the heat exchanger
by securing that there is no overlap at all of the gaps on the opposing side of the
same heat exchanger plate.
[0062] The interface between the first and second parts of the first fin structure may be
defined by an edge of the first part of the first fin structure and an edge of the
second part, wherein the edge of the first part may have an extension with a transversal
component and face the edge of the second part and the second edge may have an extension
with a transversal component and faces said edge of the first part, and wherein the
edge of the first part may be arranged in parallel with the edge of the second part.
[0063] As mentioned above, the edges may abut each other or may be positioned with a gap
therebetween. It is preferred that the abutment or gap at the interface as measured
along fin direction is constant between any given point on the transversally extending
edge of the first part to any directly opposing point on the transversally extending
edge of the second part. Directly opposing points refers to points being aligned along
the fin direction. This is advantageous as it facilitates manufacturing. It is also
advantageous since it facilitates provision of a balanced flow across the transversal
width of the heat exchanger plates since the parallel edges typically provides uniform
flow properties across the transversal width of the interface as the medium transitioning
from a respective fluid channel in the first part to a respective fluid channel in
the second part.
[0064] The edges of the first and second parts, respectively, of the first fin structure
may extend at an angle γ relative to the fin direction, the angle γ preferably being
between 95 and 130°, more preferably between 95 and 120°, or being 90°. Thus, the
interface is either oriented such that the angle γ is preferably 90° or inclined an
angle such that the angle γ is preferably between 95 and 130°, more preferably between
95 and 120°.
[0065] It may in this context be noted that the angle γ may be chosen independently from
other angles or that the angle γ may be related to an angle β formed by an interface
between a respective part of the fin structure and a distribution structure or collection
structure provided at the vicinity of the inlet respectively outlet port.
[0066] The angle β may be angled 90° relative to the fin direction. In such a case, the
edges of the first and second parts may extend at an angle γ being 90° relative to
the fin direction thereby allowing each first and second part be formed of a rectangular
piece of material being folded back and forth perpendicular to the side edges thereof.
It is however conceivable that even in case the angle β is angled 90° relative to
the fin direction, the edges of the edges of the first and second parts, respectively,
of the first fin structure may extend at an angle γ relative to the fin direction
being different from 90°. The angle γ is in such a case preferably between 95 and
130°, more preferably between 95 and 120°. The central interface of the first fin
structure on a first side of the heat exchanger plate and the central interface of
the second fin structure on the second side of the same heat exchanger plate may be
angled such that they extend in parallel with each other. In such a case it is advantageous
to take into consideration the various discussions concerning separation of the positions
along the fin direction and the impact on any overlap of any gaps thus formed. In
such a case the various discussions are applicable and are related to a line which
is slightly inclined relative to the transversal direction; namely said angle γ minus
90°. However, it is also conceivable that the central interface the first fin structure
on a first side of the heat exchanger plate and the central interface of the second
fin structure on the second side of the same heat exchanger plate are be angled such
that they extend in crossing directions. It may be noted that the two angles are preferably,
but need not be, chosen to be the same but in opposite directions. It may in this
context be noted it may be advantageous, especially if any or both of the gaps have
a significant length along the fin direction, to take into consideration the various
discussions concerning separation of the positions along the fin direction and the
impact on any overlap of any gaps thus formed. Significant length along the fin direction
may e.g., be that the along the fin direction gap is greater a complete repeat of
the folds as measured across the fin direction. However, the central interfaces extending
in crossing directions may alternatively, especially if at least one or both of the
gaps does not have a significant length along the fin direction, be used to allow
the gaps to actually cross each other since the overlap in such a case will have a
limited transversal extension compared to if the central interfaces would extend in
parallel with each other. It may in this context be noted that a design with the angle
γ being between 95 and 130°, more preferably between 95 and 120°, with the central
interfaces crossing each other may alternatively be expressed as that the angle γ
is between 95 and 130°, more preferably between 95 and 120°, on one side of the heat
exchanger plate and between 50 and 85°, preferably between 60 and 85°, on the other
side of the heat exchanger plate.
[0067] The angle β may be between 95 and 130°, more preferably between 95 and 120°, or between
50 and 85°, preferably between 60 and 85°. In one embodiment it is preferred that
the angle γ is the same as angle β. In such a case it is possible to manufacture the
fin structure from a rectangular piece of material extending substantially transversally
at a slight inclination relative to the transversal direction at an angle being the
angle β minus 90°. The leading and trailing edge of the sheet; the edges that will
extend along the longitudinal edges of the heat exchanger are in such a case trimmed
at said angle being angle β minus 90° in respective direction. If the angles β at
the distribution structure and the collection structure are different the angle γ
may be selected to be the same as one of the angles β or in case there are more than
two parts of the fin structure, the respective angle γ may be chosen to be the same
as the respective angle β and then the one or more central interfaces formed of parts
not sharing an interface with the distribution structure of collection structure having
an angle γ being chosen e.g., as one of the angles β or e.g., being 90° relative to
the fin direction. It may in this context be noted that the discussion concerning
the angle γ being chosen to be the same on both sides such that the interfaces on
the different sides are parallel or being chosen to be different on the different
sides such that the interfaces on the differents sides cross each other is equally
applicable the cases where the angle β is between 95 and 130°, more preferably between
95 and 120°, or between 50 and 85°, preferably between 60 and 85°.
[0068] This design is advantageous since it allows for a smooth transition of the flow of
medium at the interface, since it facilitates manufacture of the fin structure even
for different specific design choices when it comes to other parts of the heat exchanger
and since it results in a mechanically strong heat exchanger.
[0069] The interface between the first and second parts of the second fin structure may
be defined by an edge of the first part of the second fin structure and an edge of
the second part, wherein the edge of the first part may have an extension with a transversal
component and face the edge of the second part and the second edge may have an extension
with a transversal component and face said edge of the first part, and wherein the
edge of the first part may be arranged in parallel with the edge of the second part.
Advantages and variations of this has been discussed in relation to the corresponding
feature in respect of the first fin structure and that discussion is equally applicable
to the second fin structure.
[0070] The edges of the first and second parts, respectively, of the second fin structure
may extend at an angle γ relative to the fin direction, the angle γ preferably being
between 95 and 130°, more preferably between 95 and 120°, or being 90°. Thus, the
interface is either oriented such that the angle γ is preferably 90° or inclined an
angle such that the angle γ is preferably between 95 and 130°, more preferably between
95 and 120°. Advantages and variations of this has been discussed in relation to the
corresponding feature in respect of the first fin structure and that discussion is
equally applicable to the second fin structure.
[0071] In some embodiments, the geometries, such as the height, width, shape and/or thickness,
of the folds of the fin structures of the channels of the respective first and second
set of channels may be different from each other. Thereby it is possible to exchange
heat between two different mediums having different properties, such as different
phases, different densities, different flows, etc.
[0072] However, it may also be noted that the first and second set of channels may be designed
equal to each other.
[0073] Preferred embodiments appear in the dependent claims and in the description. It may
be noted that the use of first, second, third, fourth, fifth, etc. are mainly to be
seen as labels facilitating reading and that it does not necessarily mean that there
need to be all the intervening numbers of portions present. It may e.g., be noted
that it is contemplated to have a design where there is a first portion, a second
portion, a third portion and a fifth portion, with the fourth portion being omitted.
However, to facilitate reading, we have consistently used the numbering first, second,
third, fourth, etc., as labels, and in a sense based on an embodiment including all
conceivable portions.
[0074] Generally, all terms used in the claims are to be interpreted according to their
ordinary meaning in the technical field, unless explicitly defined otherwise herein.
All references to "a/an/the [element, device, component, means, step, etc]" are to
be interpreted openly as referring to at least one instance of said element, device,
component, means, step, etc., unless explicitly stated otherwise. The steps of any
method disclosed herein do not have to be performed in the exact order disclosed,
unless explicitly stated.
Brief description of the drawings
[0075] The above, as well as additional objects, features, and advantages of the present
disclosure, will be better understood through the following illustrative and non-limiting
detailed description of preferred embodiments of the present invention, with reference
to the appended drawings, where the same reference numerals will be used for similar
elements, wherein:
Figure 1 discloses a heat exchanger.
Figure 2 discloses a heat exchanger plate of the heat exchanger in figure 1.
Figure 3 discloses a heat exchanger plate of figure 2 with a fin structure arranged
on the plate.
Figure 4 illustrates a first cross-sectional side view of a stack of heat exchanger
plates of the heat exchanger in figure 1.
Figure 5 illustrates a second cross-sectional side view of a stack of heat exchanger
plates of the heat exchanger in figure 1.
Figure 6 discloses a portion of the plate of figures 2 and 3.
Figure 7 discloses a portion corresponding to figure 6 of a plate according to another
embodiment.
Figure 8 discloses a whole plate according to the embodiment of figure 7.
Detailed description of preferred embodiments
[0076] The present invention will now be described more fully hereinafter with reference
to the accompanying drawings, in which currently preferred embodiments of the invention
are shown. This invention may, however, be embodied in many different forms and should
not be construed as limited to the embodiments set forth herein; rather, these embodiments
are provided for thoroughness and completeness, and fully convey the scope of the
invention to the skilled person.
[0077] Figure 1 illustrates a heat exchanger 100 by way of example. The heat exchanger 100
comprises a stack of heat exchanger plates 105. The stack of heat exchanger plates
105 is formed by stacking one heat exchanger plate 107 on top of another heat exchanger
plate 107 along a stacking direction SD. The stack of heat exchanger plates 105 is
arranged between two end plates 109 (only one of the two end plates is illustrated
in the figure). It may be noted that the different embodiments disclosed herein are
in general terms useful for different combinations of fluids, such as gas-liquid,
liquid-gas, gas-gas, and liquid-liquid in the first respectively the second set of
channels. However, a skilled person will realize that some of the embodiments are
more suitable for some specific combinations of fluids than other combinations of
fluids.
[0078] The heat exchanger 100 comprises a first inlet 101 along a first longitudinally extending
side LES1 and a first outlet 111 along a second longitudinally extending side LES2.
The heat exchanger 100 further comprises a second inlet 102 along the first longitudinally
extending side LES1 and a second outlet 112 along the second longitudinally extending
side LES2. It should however be noted that the first inlet 101 may be arranged along
the second longitudinally extending side LES2 and the first outlet 111 may be arranged
along the first longitudinally extending side LES1. It should further be noted that
the second inlet 102 may be arranged along the second longitudinally extending side
LES2 and the second outlet 112 may be arranged along the first longitudinally extending
side LES1. It may however be noted that in a preferred embodiment, the first and second
inlets 101, 102 are arranged along the same longitudinally extending side and the
first and second outlets 111, 112 are arranged along the same longitudinally extending
side. The first and second longitudinally extending sides LES1, LES2 being arranged
opposite to each other.
[0079] As best illustrated in figure 4, the heat exchanger 100 further comprises a first
set of channels 401 and a second set of channels 402. The first set of channels 401
is formed in every second interspace between the heat exchanger plates 107 of the
stack of heat exchanger plates 105. The second set of channels 402 is formed in every
other interspace between the heat exchanger plates 107 of the stack of heat exchanger
plates 105.
[0080] In each channel of the first and second set of channels 401, 402 fin structures 210
are positioned in between the heat exchanger plates 107. The respective fin structure
210 abuts the heat exchanger plates 107 along a plurality of contact lines 415. The
fin structure 210 may be folded along straight lines such that the contact lines 415
extends in parallel with a longitudinally extending fin direction FD. However, as
indicated in figure 6, the fin structure 210 may alternatively be folded along lines
having other shapes. In the example of figure 6, there is shown wavy or curved lines
resulting in that the contact lines becomes wavy or curved lines undulating back and
forth along a main extension. Irrespective of the shape of the fold lines, it is preferred
that the main extension extends in parallel with a longitudinally extending fin direction.
Thereby, a plurality of fluid channels forming the first and second set of channels
401, 402 is defined. The fin structure 210 is preferably formed of sheets being folded
back and forth. As is e.g., shown in figure 4, the folds of the respective fin structure
210 are essentially being shaped as a sinus wave with elongated legs or along the
stacking direction SD. The type of structure of the respective fin structure 210 may
differ. For instance, the folds of the respective fin structure 210 may be shaped
as a square wave, a triangular wave, a sawtooth wave, or combinations thereof. The
extension of the fin structure 210 of the first set of channels 401 along the stacking
direction SD is longer than the extension of the fin structure 210 of the second set
of channels 402 along the stacking direction SD. The folds of the fin structure 210
of the first set of channels 401 are wider, as measured along the transverse direction
TD, than the folds of the fin structure 210 of the second set of channels 402. It
should however be noted that the geometries of the each of the respective fin structure
210 of each of the channels may differ. For instance, in some embodiments, the folds
of each of the fin structures 210 of each channel of the respective first set of channels
401 and second set of channels 402 may be identical. In some embodiments, the extension
of the fin structure 210 of the first set of channels 401 along the stacking direction
may be shorter than that of the fin structure 210 of the second set of channels 402.
In some embodiments, the folds of the fin structure 210 of the first set of channels
401 may be narrower than those of the fin structure 210 of the second set of channels
402. In some embodiments, the folds of the fin structures 210 of the first set of
channels 401 may be shaped as a square wave while the folds of the fin structures
210 of the second set of channels 401 may be shaped as a sawtooth wave. It should
be conceivable that each individual fin structure 210 of each channel of the first
set of channels 401 may not be identical but may vary in geometry. It should be conceivable
that each individual fin structure 210 of each channel of the second set of channels
402 may not be identical but may vary in geometry.
[0081] With reference to figure 2, a heat exchanger plate 107 of the stack of heat exchanger
plates 105 is illustrated by way of example. The heat exchanger plate 107 comprises
four through-going openings. The through-going openings are formed at a respective
corner portion of the heat exchanger plate 107. The through-going openings are configured
to form a first inlet port 201, a first outlet port 211, a second inlet port 202 and
a second outlet port 212 extending through the stack along the stacking direction
SD.
[0082] It should be noted that each heat exchanger plate 107 of the stack of heat exchanger
plates 105 comprises the first inlet port 201, the first outlet port 211, the second
inlet port 202 and the second outlet port 212. Each port 201, 202, 211, 212 extend
through the stack 105 along the stacking direction SD. The first inlet port 201 is
arranged on the first longitudinally extending side LES1 of the heat exchanger plate
107. The first outlet port 211 is arranged on the second longitudinally extending
side LES2 of the heat exchanger plate 107. The second inlet port 202 is arranged on
the first longitudinally extending side LES1 of the heat exchanger plate 107. The
second outlet port 212 is arranged on the second longitudinally extending side LES2
of the heat exchanger plate 107. Hence, the first inlet port 201 coincides with the
first inlet 101 and the first outlet port 211 coincides with the first outlet 111.
The first inlet port 201 and first outlet port 211 being in fluid connection with
each other via the first set of channels 401 formed in every second interspace. Thereby,
the first set of channels 401 form diagonally extending flow paths by having the first
inlet 101, the first outlet 111, the first inlet port 201 and the first outlet port
211 arranged as discussed above. The second inlet port 202 coincides with the second
inlet 102 and the second outlet port 212 coincides with the second outlet 112. The
second inlet port 202 and second outlet port 212 being in fluid connection with each
other via the second set of channels 402 formed in the other every second interspace.
The second set of channels 402 form diagonally extending flow path by having the second
inlet 102, the second outlet 112, the second inlet port 202 and the second outlet
port 212 arranged as discussed above.
[0083] The heat exchanger 100 further comprises, in each space between the heat exchanger
plates 107, a distribution structure 220 at the respective inlet port 201, 202 and
a collection structure 230 at the respective outlet port 211, 212. The respective
distribution structure 220 is positioned between the respective inlet port 201, 202,
and the respective fin structure 210 in the respective first and second set of channels
401, 402. The respective collection structure 230 is positioned between the respective
outlet port 211, 212, and the respective fin structure 210 in the respective first
and second set of channels 401, 402.
[0084] An interface 227, also referred to as a port interface 227, between the respective
inlet port 201, 202 and the respective distribution structure 220 is inclined relative
to the fin direction FD. Thereby, a distance between the interface 227 and the fin
structure 210, as measured along the fin direction FD, increases with increasing distance,
as seen along an imaginary line extending across the fin direction FD. The distance
along the fin direction FD increases as one follows the imaginary line from an edge
121 of the respective heat exchanger plate 107 which is closest to the respective
inlet port 201, 202 and which extends along the fin direction FD. An interface 237,
also referred to as a port interface 237, between the respective outlet port 211,
212 and the respective collection structure 230 is inclined relative to the fin direction
FD. Thereby, a distance between the interface and the fin structure 210, as measured
along the fin direction FD, increases with increasing distance, as seen along an imaginary
line extending across the fin direction FD. The distance along the fin direction FD
increases from as one follows the imaginary line from an edge 122 of the respective
heat exchanger plate 107 which is closest to the respective outlet port 211, 212 and
which extends along the fin direction FD.
[0085] Although figure 2 only illustrates the port interface 227 between the first inlet
port 201 and the distribution structure 220, it should be clearly understood by the
skilled person that in practice, the port interface between the second inlet port
202 and the distribution structure 220 is designed in a similar way as discussed above.
Further, although figure 2 only illustrates the port interface 237 between the first
outlet port 211 and the collection structure 230, it should be clearly understood
by the skilled person that in practice, the port interface between the second outlet
port 212 and the collection structure 230 is designed in a similar way as discussed
above.
[0086] The respective port interface forms an angle α with the fin direction FD. It may
be noted that in a preferred embodiment, the angle α is between 110 and 160°, preferably
between 120 and 150°.
[0087] The distribution structure 220 is formed as a triangular or truncated triangular
distribution structure. It should be noted that in the distribution structure, the
fins or folds extends along an internal fin direction being diagonally arranged relative
to the fin direction FD of the fin structure 210. Basically, the fins or folds of
the distribution structure 220 extends between the respective inlet port and the fin
structure 210 along said internal fin direction. The fins or folds as such may be
vertically arranged as viewed along its diagonal extension. The fins or folds of the
distribution structure 220 may basically be of any kind discussed above in relation
to the fin structure 210 with the fin direction referring to its diagonally extending
internal fin direction.
[0088] The collection structure 230 is formed as a triangular or truncated triangular collection
structure. Preferably, the collection structure 230 is formed by a triangular or truncated
triangular fin structure such that the collection structure 230 has the similar design
as the distribution structure 220. It should be noted that in the collection structure
230 the fins or folds extends along an internal fin direction being diagonally arranged
relative to the fin direction FD of the fin structure 210. The fins or folds of the
collection structure 230 may basically be of any kind discussed above in relation
to the fin structure 210 with the fin direction referring to its diagonally extending
internal fin direction. Depending upon the positioning of the different ports, the
internal diagonally extending fin direction of the distribution structure 220 and
the collection structure 230 may be basically in the same orientation or in crossing
directions. The fins or folds as such may be vertically arranged as viewed along its
diagonal extension. The fins or folds of the collection structure 230 may basically
be of any kind discussed above in relation to the fin structure 210 with the fin direction
referring to its diagonally extending internal fin direction. Depending upon the positioning
of the different ports, the internal diagonally extending fin direction of the distribution
structure 220 and the collection structure 230 may be basically in the same orientation
or in crossing directions.
[0089] One edge of the distribution structure 220 extends from a first corner 223 of the
first inlet port 201 towards a second corner 224 of the inlet port 201. The first
corner 223 may be referred to as a transversally central corner and the second corner
224 may be referred to as a transversally outer corner. As illustrated e.g., in figures
3, 5 and 6, the distribution structure 220 extends towards the second corner 224 but
not all the way to the second corner 223. This leaves a transversally extending gap
225 at a longitudinally extending edge 121 which is closest to the first inlet port
201. With such a design, a major portion of a flow from the first inlet port 201 is
distributed via the distribution structure 220 to the fin structure 210. Further,
with such a design, a minor portion of the flow from the first inlet port 201 is transferred
to the fin structure 210 via the gap 225. However, it may be noted that the distribution
structure 220 may extend all the way to the second corner 223.
[0090] One edge of the collection structure 230 extends form a first corner 233 of the first
outlet port 211 towards a second corner 234 of the outlet port 211. The first corner
233 may be referred to as a transversally central corner of the first outlet port
211 and the second corner 234 may be referred to as a transversally outer corner of
the first outlet port 211. As illustrated, the collection structure 230 extends towards
the second corner 234 but not all the way to the second corner 234. This leaves a
transversally extending gap 235 at a longitudinally extending edge 122 which is closest
to the first outlet port 211. With such a design, a major portion of a flow is collected
via the collection structure 230 to the first outlet port 211. Further, with such
a design, a minor portion of the flow from the fin structure 210 is transferred to
the first outlet port 211 via the gap 235. However, it may be noted that the collection
structure 230 may extend all the way to the second corner 234.
[0091] The second inlet port 202 is preferably designed in a similar way as the first inlet
port 201 as discussed above and the second outlet port 212 is preferably designed
in a similar way as the first outlet port 202 as discussed above.
[0092] As further depicted in figure 2, the respective inlet ports 201, 202 are designed
as asymmetric inlet ports i.e., the dimensions of the first respective second inlet
port 201, 202 is different. This is because the respective inlet port 201, 202 is
designed to supply different flows of medium to its respective distribution structure
220 and to its respective fin structure 210. It may be noted that in a preferred embodiment,
and as illustrated in the figure, the first inlet port 201 and the second inlet port
202 have a triangular shape. This is to match the inlet ports 201, 202 with the respective
distribution structure in an easy and efficient way. The respective outlet ports 211,
212 are designed as asymmetric outlet ports i.e., the dimensions of the first respective
second outlet port 211, 212 is different. This is because the respective outlet port
211, 212 is designed to receive different flows of medium from its respective collection
structure 230. It may be noted that in a preferred embodiment, and as illustrated
in the figure, the first outlet port 211 and the second outlet port 212 have a triangular
shape. This is to match the outlet ports 211, 212 with the respective distribution
structure in an easy and efficient way. It may be noted that in a preferred embodiment,
and as illustrated, the respective port 201, 202, 211, 212 is arc-shaped along at
least a major portion of a transversal extension of the gap.
[0093] As is shown in figure 3 and also in figures 6-8, an internal interface 228 between
the respective distribution structure 220 and the fin structure 210 in the respective
channel of the first set of channels 401 is inclined relative to the longitudinally
extending fin direction FD and is inclined also relative to a transversal direction
TD. The internal interface 228 forms an angle β with the fin direction FD. The angle
β is between 95 and 130°, preferably between 95 and 120°, or between 50 and 85°, preferably
between 60 and 85°. In figures 3 and 6, there is disclosed a design where the angle
β is between 95 and 130°, preferably between 95 and 120°. In figures 7 and 8, there
is disclosed a design where the angle β is between 50 and 85°, preferably between
60 and 85°.
[0094] As shown in figures 3 and 8, an internal interface 238 between the respective collection
structure 230 and the fin structure 210 in the respective channel of the first set
of channels 401 is inclined relative to the longitudinally extending fin direction
FD and is inclined also relative to a transversal direction TD. The internal interface
238 forms an angle β with the fin direction FD. The angle β is between 95 and 130°,
preferably between 95 and 120°, or between 50 and 85°, preferably between 60 and 85°.
In figures 3 and 6, there is disclosed a design where the angle β is between 95 and
130°, preferably between 95 and 120°. In figure 8, there is disclosed a design where
the angle β is between 50 and 85°, preferably between 60 and 85°.
[0095] On the opposite side of the plate 107, an internal interface 228 between the respective
distribution structure 220 and the fin structure 210 in the respective channel of
the second set of channels 402 is inclined relative to the longitudinally extending
fin direction FD and is inclined also relative to a transversal direction TD. The
internal interface 228 forms an angle β with the fin direction FD. The angle β is
between 95 and 130°, preferably between 95 and 120°, or between 50 and 85°, preferably
between 60 and 85°.
[0096] In figures 3 and 6, there is disclosed a design where the angle β on said opposite
side is also between 95 and 130°, preferably between 95 and 120°. That is, in the
design of figures 3 and 6, the internal interface 228 on the side shown in the figures
and the internal interface on the opposite side have a similar inclination. In figures
7 and 8, there is disclosed a design where the angle β is between 50 and 85°, preferably
between 60 and 85° on the side visible in said figures and where the angle β is between
95 and 130°, preferably between 95 and 120°. That is, in the design of figures 7 and
8, the internal interface 228 on the side shown in the figures and the internal interface
228 on the opposite side have a opposite inclinations.
[0097] The above discussion concerning the directions of the internal interfaces 228 on
the opposite sides is equally applicable in respect of the internal interfaces 238
on the opposite sides.
[0098] As is shown in figures 3, and 6-8, the respective internal interface 228, 238 preferably
extends along a substantially straight line.
[0099] In the embodiments shown in figures 3, and 6-8, the internal interface 228 at the
first inlet port 201 and the internal interface 238 at the first outlet port 211 are
inclined in the same direction relative to the transverse direction TD. In the preferred
embodiment, also the angle β is the same for the two internal interfaces 228, 238
of the first channel 401. In the preferred embodiment also the internal interface
228 at the second inlet port 202 and the internal interface 238 at the second outlet
port 212 are inclined in the same direction relative to the transverse direction TD.
As mentioned above, this "same direction" refers to the directions of the internal
interfaces 228, 238 of the same channel and that the directions may be the same or
be different on the opposite sides of the plate 107. In the preferred embodiment,
also the angle β is the same of the two internal interfaces 228, 238 of the second
channel 402.
[0100] As e.g., shown in figure 3 and 5, a first fin structure 210a in a first channel of
the first set of channels 401 comprises a first part 210a1and a second part 210a2.
The first and second part 210a1-2 are arranged one after the other along the fin direction
FD. Hence, an interface is formed between the first and second part 210a1-2 by a transversally
extending side or edge of the first part 210a1 being directly opposite to a transversally
extending side or edge of the second part 210a2. This interface may also be referred
to as a central interface. It may in this context be noted that the word central is
a label facilitating differentiation from other interfaces and that the word used
as a label could also be e.g., a third interface. The transversally extending sides
or edges are arranged in parallel with each other. The interface extends across the
fin direction. The transversally extending sides of the respective first and second
part 210a1-2 extend at an angle γ with respect to the fin direction. In preferred
embodiments, the transversally extending sides or edges of the respective first and
second part 210a1-2 extend at 90° with respect to the fin direction. The interface
is positioned at a first position P1 along the fin direction. The interface is positioned
by choosing the dimensions of the first and second parts 210a1-2. It may be noted
that the edges of the first and second parts 210a1-2, respectively, of the first fin
structure 210a may alternatively extend at an angle γ relative to the fin direction
FD, where the angle γ is between 95 and 130°, preferably between 95 and 120°. It is
conceivable that the interface is formed of the edges abutting each other and it is
conceivable that the interface includes a gap.
[0101] As e.g., shown in figure 5, a second fin structure 210b in a first channel of the
second set of channels 402 comprises a first and a second part 210b1-2. The first
and second part 210b1-2 are arranged one after the other along the fin direction.
Hence, an interface is formed between the first and second part 210b1-2 by a transversally
extending side or edge of the first part 210b1 being directly opposite to a transversally
extending side or edge of the second part 210b2. The transversally extending sides
or edges are arranged in parallel with each other. The interface extends across the
fin direction. The transversally extending sides or edges of the respective first
and second part 210b1-2 extend at an angle γ with respect to the fin direction FD.
In preferred embodiments, the transversally extending sides of the respective first
and second part 210b1-2 extend at 90° with respect to the fin direction. The interface
is positioned at a second position P2 along the fin direction. The interface is positioned
by choosing the dimensions of the first and second parts 210b1-2. It may be noted
that the edges of the first and second parts 210b1-2, respectively, of the second
fin structure 210b may alternatively extend at an angle γ relative to the fin direction
FD, where the angle γ is between 95 and 130°, preferably between 95 and 120°. It is
conceivable that the interface is formed of the edges abutting each other and it is
conceivable that the interface includes a gap.
[0102] Figure 5 illustrates a stack of heat exchanger plates 105 and a stack of a set of
first channels 401 and a second set of channels 402. The first and second positions
P1, P2 of the interfaces are separated a distance DP from each other along the fin
direction. The distance DP between the first and second positions P1, P2 is such that
any longitudinal gap G1 at the central interface 239a between the first and second
part 210a1-2 in the first channel of the first set of channels 401 at least does not
overlap a midline of any longitudinal gap G2 at the central interface 239b between
the first and second part 210b1-2 in the first channel of the second set of channels
402, and vice versa.
[0103] It is preferred that any gap between the first and second part 210a1-2 in the first
channel of the first set of channels 401 does not overlap with any gap between the
first and second parts 210b1-2 in the first channel of the second set of channels
402. In figure 4, the dimensions of the first and second parts 210a1-2 in the first
channel of the first set of channels 401 have been chosen such that the gap therebetween
does not overlap with any gap between the first and second parts 210b1-2 in the first
channel of the second set of channels 402. It may be noted that fin structures 210
not being neighbouring fin structures 210 may comprise parts 210a1-2, 210b1-2 with
identical dimensions. That is, there may be gaps overlapping each other as long as
the gaps are not formed on opposite sides of the same heat exchanger plate.
[0104] The person skilled in the art realizes that the present invention by no means is
limited to the preferred embodiments described above. On the contrary, many modifications
and variations are possible within the scope of the appended claims. Additionally,
variations to the disclosed embodiments may be understood and effected by the skilled
person practicing the claimed invention, from a study of the drawings, the disclosure,
and the appended claims.
1. A heat exchanger (100) comprising a stack of heat exchanger plates (105) stacked one
on top of the other along a stacking direction (SD),
a first set of channels (401) formed in every first second interspace between the
heat exchanger plates (107),
a second set of channels (402) formed in every second second interspace between the
heat exchanger plates (107),
wherein, in each of the channels in the first and second set of channels (401, 402)
fin structures (210) formed of sheets being folded back and forth are positioned between
the heat exchanger plates (107) such that the respective fin structure (210) abuts
the heat exchanger plates (107) along a plurality of contact lines (415) having a
main extension extending in parallel with a longitudinally extending fin direction
(FD) thereby defining plurality of fluid channels forming said first and second set
of channels (401, 402),
wherein each heat exchanger plate (107) comprises four through-going openings (201,
202, 211, 212) formed at a respective corner portion of the respective heat exchanger
plate (107) and configured to form a first inlet port (201) extending through the
stack (105) along the stacking direction (SD), a first outlet port (211) extending
through the stack (105) along the stacking direction (SD), a second inlet port (202)
extending through the stack (105) along the stacking direction (SD), and a second
outlet port (212) extending through the stack (105) along the stacking direction (SD),
the first inlet port (201) and first outlet port (211) being in fluid connection with
each other via the first set of channels (401) and the second inlet port (202) and
second outlet port (212) being in fluid connection with each other via the second
set of channels (402),
wherein the heat exchanger (100) further comprises, in each interspace between the
heat exchanger plates (107), a distribution structure (220) at the respective inlet
port (201, 202) and a collection structure (230) at the respective outlet port (211,
212),
wherein the respective distribution structure (220), respectively the respective collection
structure (230) is positioned between the respective port (201, 202, 211, 212) and
the respective fin structure (210) in the respective first and second set of channels
(401, 402),
wherein an internal interface (228) between the respective distribution structure
(220) and the fin structure (210) and/or an internal interface (238) between the respective
collection structure (230) and the fin structure (210) in the respective channel of
the first set of channels (401) and/or in the respective channel of the second set
of channels (402) is inclined relative to the longitudinally extending fin direction
(FD) and is inclined also relative to a transversal direction (TD).
2. The heat exchanger (100) according to claim 1, wherein the respective internal interface
(228, 238) forms an angle β with the fin direction (FD), wherein the angle β is between
95 and 130°, preferably between 95 and 120°, or between 50 and 85°, preferably between
60 and 85°.
3. The heat exchanger (100) according to any one of the preceding claims, wherein the
respective internal interface (228, 238) extends along a substantially straight line.
4. The heat exchanger (100) according to any one of the preceding claims, wherein the
internal interface (228) at the respective inlet port (201, 202) and the internal
interface (238) at the respective outlet port (211, 212) is inclined in the same direction
relative to the transverse direction (TD).
5. The heat exchanger (100) according to any one of the preceding claims, wherein a port
interface (227) between the respective inlet port (201, 202) and the respective distribution
structure (220), respectively a port interface (235) between the respective outlet
port (211, 212) and the collection structure (230) is inclined relative to the fin
direction (FD) such that a distance between the port interface (227, 235) and the
fin structure (210), as measured along the fin direction (FD), increases with increasing
distance, as seen along an imaginary line extending transversally across the fin direction
(FD), from an edge (121, 122) of the respective heat exchanger plate (107) which is
closest to the respective port (201, 202, 211, 212) and which extends along the longitudinally
extending fin direction (FD).
6. The heat exchanger (100) according to claim 5, wherein the respective port interface
forms an angle (α) with the fin direction (FD), wherein the angle (α) is between 110
and 160°, preferably between 120 and 150°.
7. The heat exchanger (100) according to claim 5 or 6, wherein the respective port interface
extends along a substantially straight line.
8. The heat exchanger (100) according to any one of claims 5-7, wherein the respective
distribution structure (220), and/or the respective collection structure (230), extends
from a first, transversally central, corner (223, 233) of the respective port (201,
202, 211, 212) towards a second, transversally outer, corner (224, 234) of the respective
port (201, 202, 211, 212) and leaves a transversally extending gap (225, 235) at the
longitudinally extending edge (224, 234) being closest to the respective port (201,
202, 211, 212).
9. The heat exchanger (100) according to claim 8,
wherein a major portion of a flow from the respective inlet port (201, 202) is distributed
via the distribution structure (220) to the fin structure (310), respectively a major
portion of a flow from the fin structure (310) is collected via the collection structure
(230) to the respective outlet port (211, 212); and
wherein a minor portion of the flow from the respective inlet port (201, 202) is transferred
to the fin structure (310) via said gap (235), respectively a minor portion of the
flow from the fin structure (310) is transferred to the respective outlet port (211,
212) via said gap (235).
10. The heat exchanger (100) according to claim 8 or 9, wherein a cut in the respective
heat exchanger plate (107) forming respective port (201, 202, 211, 212) is arc-shaped
along at least a major portion of a transversal extension of said gap (225, 235).
11. The heat exchanger (100) according to any one of claims 5-10, wherein the distribution
structure (220) and/or the collection structure (230) is formed by a basically triangular
or truncated triangular fin structure.
12. The heat exchanger (100) according to any one of the preceding claims, wherein the
respective ports (201, 202, 211, 212) are formed as substantially triangular ports.
13. The heat exchanger (100) according to any one of the preceding claims, wherein the
first inlet port (201) is arranged on a first longitudinally extending side (LES1)
of the stack of heat exchanger plates (105) and the first outlet port (211) is arranged
on a second longitudinally extending side (LES2) of the stack of heat exchanger plates
(105), the second longitudinally extending side (LES2) being opposite the first longitudinally
extending side (LES1), and
wherein the second inlet port (202) is arranged on the first longitudinally extending
side (LES1) of the stack of heat exchanger plates (105) and the second outlet port
(212) is arranged on the second longitudinally extending side (LES2) of the stack
of heat exchanger plates (105), the first longitudinally extending side (LES1) being
opposite the second longitudinally extending side (LES2).
14. The heat exchanger (100) according to any one of the preceding claims, wherein, in
a first channel of the first set of channels (401), a first fin structure (210a) comprises
at least a first and a second part (210a1-2) arranged one after the other along the
fin direction (FD),
wherein, in a first channel of the second set of channels (402), the first channel
of the second set of channels (402) being a neighbouring channel to the first channel
of the first set of channels (401), a second fin structure (210b) comprises at least
a first and a second part (210b1-2) arranged one after the other along the fin direction
(FD),
wherein a central interface (239a) between the first and second parts (210a1-2) of
the first fin structure (210a) extends across the longitudinal fin direction (FD)
and is positioned at a first position (P1) along the fin direction (FD),
wherein a central interface (239b) between the first and second parts (210b1-2) of
the second fin structure (210b) extends across the fin direction (FD) and is positioned
at a second position (P2) along the fin direction (FD), and
wherein the first and second positions (P1, P2) are separated a longitudinal distance
(DP) from each other.
15. A heat exchanger (100) according to any one of the preceding claims, wherein the distance
(DP) between the first and second positions (P1, P2) is such that any longitudinal
gap (G1) at the central interface (239a) between the first and second part (210a1-2)
in the first channel of the first set of channels (401) at least does not overlap
a midline of any longitudinal gap (G2) at the central interface (239b) between the
first and second part (210b1-2) in the first channel of the second set of channels
(402), and vice versa, wherein preferably the distance (DP) between the first and
second positions (P1, P2) is such that any longitudinal gap (G1) at the central interface
(239a) between the first and second part (210a1-2) in the first channel of the first
set of channels (401) does not overlap with any longitudinal gap (G2) at the central
interface (239b) between the first and second part (210b1-2) in the first channel
of the second set of channels (402), and vice versa.