Note: Descriptions are shown in the official language in which they were submitted.
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Description
Heat exchanger having channels for damping liquid motions
The invention relates to a heat exchanger for indirect heat transfer between a
first
medium and a second medium according to claim 1.
Such a heat exchanger generally has a shell, which defines a shell space for
receiving a liquid phase of the first medium, and at least one heat exchanger
block
(also referred to as the "core"), which has first heat transfer passages for
receiving
the first medium and second heat transfer passages for receiving the second
medium, so that heat can be transferred indirectly between the two media,
wherein the heat exchanger block is arranged in the shell space in such a way
that it can be surrounded by a liquid phase of the first medium that is
located in
the shell space.
Such a heat exchanger is shown for example in Figure 9-1 in "The standards of
the brazed aluminum plate-fin heat exchanger manufacturer's association
(ALPEMA)", third edition, 2010, page 67. Such a configuration of a heat
exchanger is also referred to as a "core-in-shell" or "block-in-shell" heat
exchanger.
The driving force for the flow of the first medium (for example refrigerant)
through
the at least one heat exchanger block is preferably produced by the
thermosiphon
effect caused by the vaporization. However, the shell space of the heat
exchanger
not only fulfils the purpose of a storage tank but also serves as a separating
apparatus for separating the generated steam of the first medium from the
refrigerant liquid or the liquid phase of the first medium. For system-related
reasons, therefore, a free surface of the liquid phase of the first medium
forms in
the shell space. The shell of the heat exchanger, which is preferably
cylindrically
formed, may in this case be aligned both horizontally and vertically as far as
the
orientation of the longitudinal axis or cylinder axis is concerned. The heat
exchanger block is in principle mainly flowed through upwardly by the
refrigerant
liquid. In particular, the direction of throughflow of the stream to be cooled
down
(second medium) is not restricted.
If the heat exchanger is to be set up on a movable base, for example a
floating
body (for example a ship), the generally known problems that sometimes occur
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with liquid-filled containers can therefore arise, in particular that the
liquid in the
container or the shell space can move back and forth, so that for example
levels
varying over time are obtained at a number of locations in the shell space. As
a
result, for example, the depth of immersion of the heat exchanger blocks in
the
liquid phase of the first medium varies, which can for example impair the
effectiveness of the heat transfer. As far as possible, the liquid motion of
the bath
must therefore be damped to the extent that safe and reliable operation can be
ensured.
Against this background, the object of the present invention is therefore that
of
providing a heat exchanger of the type mentioned at the beginning that
alleviates
the aforementioned difficulty.
This problem is solved by a heat exchanger with the features of claim 1.
It is accordingly provided that a plurality of cylindrical channels for
conducting the
first medium that run parallel to one another and in particular are only in
flow
connection with, or can be flowed through by, the bath or the liquid phase are
provided in the shell space laterally in relation to the at least one heat
exchanger
block.
Cylindrical means here, in the general sense, that the base area of the
cylinder,
which in the present case is the cross-sectional area of the channel, may have
any desired planar area, which may in particular be formed in a circular
(circular
cylinder), rectangular, square, triangular or hexagonal manner. The respective
cylinder is in this case produced by displacing that planar area along a
straight
line or longitudinal axis that does not lie in the plane of the planar area
and
preferably extends normal to that planar area or cross-sectional area.
The individual channels are also preferably separated from one another over
their
circumference by wallings, to be precise preferably in the form of peripheral
wallings, in particular completely closed wallings. In the case of such
completely
closed wallings, the medium that flows along the longitudinal axis of the
channel in
the respective channel cannot enter a neighboring channel (transversely in
relation to the longitudinal axis).
It is possible that one channel, several channels or all channels has/have a
separate, peripheral walling of their own. There is also the possibility that
a walling
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of a channel also forms part of a walling of a neighboring channel. This may
also
apply to a number of channels or to all channels.
On the basis of the solution according to the invention, the liquid phase of
the first
medium in the shell space of the heat exchanger can advantageously be stilled
when there are fluctuating movements of the heat exchanger. A fluctuating
movement is understood in this case as being in particular a movement in which
the longitudinal axis or cylinder axis of the shell changes its spatial
position or
inclination, in particular periodically (for example on account of the swell
when the
heat exchanger is arranged on a floating body on a body of water).
If - with respect to a heat exchanger arranged as intended, which from now on
is
assumed - the channels are for example aligned along the vertical, during the
operation of the heat exchanger the liquid phase can escape at the upper end
of
the heat exchanger block and flow back down again through the channels
laterally
in relation to the heat exchanger block. The channels in this case represent a
flow
resistance in the horizontal direction, which suppresses a motion of the
liquid
phase of the first medium along the horizontal.
In the case of horizontally oriented channels, during fluctuating movements of
the
heat exchanger the liquid phase in the channels may possibly flow back and
forth,
the channels likewise acting as flow resistances in the horizontal direction
on
account of the limited flow cross section, and therefore damping a
corresponding
motion of the liquid phase of the first medium. If the longitudinal axes of
the
parallel channels are aligned horizontally, a liquid motion resulting from a
fluctuating movement in which the inclination of the longitudinal axes changes
is
especially damped.
The at least one heat exchanger block may in principle be any one of all
possible
heat exchangers that can transfer heat, particularly indirectly, from the
second
medium to the first medium.
However, the heat exchanger block is preferably a plate heat exchanger. Such
plate heat exchangers generally have a plurality of plates or sheets that are
arranged parallel to one another and form a multiplicity of heat transfer
passages
for media involved in the heat transfer. A preferred embodiment of a plate
heat
exchanger has a plurality of heat directing structures, for example in the
form of
sectionally meandering, in particular corrugated or folded, sheets (known as
fins),
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which are respectively arranged between two parallel separating plates or
sheets
of the plate heat exchanger, the two outermost layers of the plate heat
exchanger
being formed by cover plates. In this way, between every two separating plates
or
between a separating plate and a cover plate there are formed, as a result of
the
fins respectively arranged in between, a multiplicity of parallel channels or
a heat
transfer passage, through which a medium can flow. Therefore, a heat transfer
can take place between the media flowing in neighboring heat transfer
passages,
the heat transfer passages that are assigned to the first medium being
referred to
as first heat transfer passages and the heat transfer passages that are
assigned
to the second medium being correspondingly referred to as second heat transfer
passages.
Provided to the sides, between every two neighboring separating plates or
between a cover plate and the neighboring separating plate, there are
preferably
terminal bars (known as side bars) for closing the respective heat transfer
passage. The first heat transfer passages are open upwardly and downwardly
along the vertical and in particular are not closed by terminal bars, so that
the
liquid phase of the first medium can enter the first heat transfer passages
from
below and can leave the first heat transfer passages as a liquid and/or
gaseous
phase at the top of the plate heat exchanger.
The cover plates, separating plates, fins and side bars are preferably
produced
from aluminum and are for example brazed to one another in a furnace. Using
appropriate headers with nozzles, media, such as for example the second
medium, can be introduced into the assigned heat transfer passages and drawn
off from them.
The shell of the heat exchanger may in particular have a peripheral, (circular-
)cylindrical walling, which with a heat exchanger arranged as intended is
preferably aligned in such a way that the longitudinal axis or cylinder axis
of the
walling or of the shell extends along the horizontal or along the vertical. At
the end
faces, the shell preferably has walls that are opposite one another, are
connected
to the walling referred to and extend transversely in relation to the
longitudinal axis
or cylinder axis.
With regard to the operating mode of the heat exchanger, as already explained
at
the beginning, it is preferably provided that the at least one plate heat
exchanger
is designed to cool down and/or at least partially liquefy the second medium,
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conducted in the second heat transfer passages, with respect to the first
medium,
conducted in the neighboring first heat transfer passages, so that a gaseous
phase of the first medium forms, the shell space being designed for collecting
the
gaseous phase.
It is preferably also provided that the at least one plate heat exchanger is
designed in such a way that during the operation of the heat exchanger the
first
medium rises up in the at least one plate heat exchanger, specifically in
first heat
transfer passages provided for this purpose of the at least one plate heat
exchanger, the at least one plate heat exchanger in particular being designed
for
conducting the second medium in the second heat transfer passages in counter-
flow or in cross-flow in relation to the first medium. The liquid phase of the
first
medium leaving at the upper end of the plate heat exchanger together with the
gaseous phase flows downward again, possibly in the vertically oriented
channels,
at the sides of the plate heat exchanger.
According to a preferred embodiment of the invention, it is provided that the
channels or the wallings thereof are fixed to one another in such a way that
they
form an interlinked unit, which is also referred to as a register. This unit
is
preferably formed separately from the heat exchanger block and/or shell.
Furthermore, according to a preferred embodiment of the invention, it is
provided
that the channels, or at least some of the channels, are formed as extending
longitudinally along their respective longitudinal axis (or cylinder axis),
i.e. the
extent along the respective longitudinal axis is greater than the greatest
inside
diameter of the respective channel perpendicularly in relation to the
respective
longitudinal axis.
The channels can consequently be flowed through by the liquid phase of the
first
medium along their respective longitudinal axis or cylinder axis, respectively
having at each of the two end faces an opening by way of which the liquid
phase
can enter and leave the respective channel. The two openings of a channel in
this
case lie opposite one another along the longitudinal axis or cylinder axis of
the
respective channel, that is to say are in line with one another.
According to a preferred embodiment of the invention, it is provided that -
with
respect to the longitudinal axes - all of the channels have the same length.
As an
alternative to this, according to a preferred configuration of the invention,
it is
,
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provided that - with respect to the longitudinal axes - some or all of the
channels
have different lengths to adapt the unit to a curved region of an inner side
of the
shell of the heat exchanger. This allows a stepped graduation of an outer side
of
the composite unit that follows the profile of the inner side region (for
example in
the case of a hollow cylindrical shell) to be achieved.
There is in principle the possibility of fixing the unit arranged in the shell
space to
the shell, so that in particular it does not contact the at least one heat
exchanger
block. As an alternative to this, the unit may also be fixed to the at least
one heat
exchanger block or to a separate carrier.
According to one configuration of the invention, it is provided with
particular
preference that the respective channel is formed by a hollow profile. The
hollow
profile, which is preferably produced from a metal (such as for example
aluminum
or steel), in this case forms a walling surrounding the respective channel and
thereby delimits or forms the respective channel. The hollow profiles are
preferably connected to one another in such a way that the interlinked unit
referred to is formed. The hollow profiles may in this case be welded to one
another or be suitably fixed to one another by other fastening means, so that
the
unit or hollow-profile register referred to is created.
According to a further embodiment of the invention, the channels are formed by
a
plurality of interconnected plate-shaped elements (for example sheets). These
elements may be formed as planar (for example planar sheets) or else have a
structure (for example the elements referred to may be formed as cross-
sectionally corrugated or folded or stepped or serrated elements/sheets). The
individual elements may for example be fixed to one another by being fitted
one
into the other and may possibly be additionally secured to one another. Brazed
and/or welded connections, riveted connections or other interlocking,
frictionally
engaging and/or material-bonding connections are conceivable for example for
the fixing or securing.
According to a preferred embodiment of the invention, it is provided that -
once
again with respect to a heat exchanger arranged as intended - the longitudinal
axes of the channels run parallel to the vertical. In this case, with a lying
shell the
longitudinal axes of the channels can run perpendicularly in relation to the
longitudinal axis or cylinder axis of the shell. With a standing shell, the
longitudinal
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axes of the vertical channels preferably run parallel to the longitudinal axis
or
cylinder axis of the shell.
According to an alternative preferred embodiment of the invention, it is
provided
that - once again with respect to a heat exchanger arranged as intended - the
longitudinal axes of the channels run parallel to the horizontal. In this
case, with a
lying shell, the longitudinal axes of the channels can run parallel to the
longitudinal
axis or cylinder axis of the shell. With a standing shell, the longitudinal
axes of the
horizontal channels preferably run perpendicularly in relation to the
longitudinal
axis or cylinder axis of the shell.
According to a preferred embodiment of the invention, it is also provided
that, with
horizontally running channels, at least some of the channels have a flow
retarder
or are closed in order to bring about a specific effect on the liquid phase.
According to a preferred embodiment of the invention, it is also provided that
the
unit or possibly the channels has or have along the vertical a length that is
at least
greater than half the height of the at least one plate heat exchanger or heat
exchanger block along the vertical, preferably greater than or equal to the
height
of the at least one plate heat exchanger or heat exchanger block along the
vertical.
It may also be provided in the case of horizontal channels that they are
shorter
along their longitudinal axis than the length of the possibly laterally
arranged heat
exchanger block along the same direction.
The unit made up of a number of channels or hollow profiles is preferably
arranged between the at least one heat exchanger block and the shell or a
portion
or inner side region of the shell that lies horizontally opposite the block.
If a number of separate heat exchanger blocks are arranged in the shell space
the
unit may also be arranged between two such blocks.
Finally, both in the case of a heat exchanger block and in the case of a
number of
heat exchanger blocks, a number of units each with a plurality of channels may
be
provided, the respective unit then preferably being arranged between one of
the
heat exchanger blocks and the shell (see above) or between two neighboring
heat
exchanger blocks.
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The respective unit may in this case be designed in the way described above.
The
further heat exchanger blocks are in turn preferably designed as plate heat
exchangers, in particular in the form described above.
Further details and advantages of the invention are to be explained by the
following descriptions of figures of exemplary embodiments on the basis of the
figures. Advantageous embodiments of the invention are also specified in the
subclaims.
In the figures:
Figure 1 shows a schematic, partially sectional view of a heat exchanger
according to the invention with a standing shell and vertical channels,
Figure 2 shows a plan view in the form of a detail of the vertical channels
shown in Figure 1;
Figure 3 shows a schematic, partially sectional view of a further heat
exchanger
according to the invention with a lying shell and vertical channels;
Figure 4 shows a schematic, partially sectional view of a heat exchanger
according to the invention with a standing shell and horizontal
channels,
Figure 5 shows a plan view in the form of a detail of the horizontal channels
shown in Figure 4;
Figure 6 shows a schematic, partially sectional view of a further heat
exchanger
according to the invention with a lying shell and horizontal channels;
and
Figure 7 shows a schematic sectional view of two heat transfer passages of a
plate heat exchanger such as can be used in the case of Figures 1, 3,
4 and 6.
Figure 1 shows in conjunction with Figure 2 a heat exchanger 1, which has a
standing, preferably (circular-)cylindrical shell 2, which delimits a shell
space 3 of
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the heat exchanger 1. The shell 2 has in this case a peripheral, cylindrical
walling
14, which is delimited at the end faces by two walls 15 lying opposite one
another.
The longitudinal axis or cylinder axis of the shell 2 coincides with the
vertical z.
Arranged horizontally next to one another in the shell space 3 enclosed by the
shell 2 there are in the present case two heat exchanger blocks 4, 5, which
are
plate heat exchangers 4, 5 that have a number of parallel heat transfer
passages
P, P' (cf. Figure 7).
The respective plate heat exchanger 4, 5 has in this case a plurality of heat
directing structures 41, which may be sheets that are formed in cross section
as
meandering, that is to say for example corrugated, serrated or with a
rectangular
profile. These structures 41 are also referred to as fins 41 and are
respectively
arranged between two planar separating plates or sheets 40 of the plate heat
exchanger 4, 5. In this way, between every two separating plates 40 (or a
separating plate and a cover plate, see below) there are formed a multiplicity
of
parallel channels or there is formed a heat transfer passage P, P', through
which
the respective medium Ml, M2 can flow. The two outermost layers 40 are formed
by cover plates of the plate heat exchanger 4, 5; provided to the sides,
between
every two neighboring separating plates or separating and cover plates 40,
there
are terminal bars 42. Figure 7 shows by way of example in the form of a detail
a
first heat transfer passage P for the first medium Ml, which is formed by a
fin 41
and two adjacent separating plates 40, and a neighboring second heat transfer
passage P' for the second medium M2, which is likewise formed by a fin 41 and
two adjacent separating plates 40. Such an arrangement of passages is
preferably repeated in the respective plate heat exchanger 4, 5, so that a
number
of first and second heat transfer passages P, P' are arranged next to one
another
in an alternating manner.
During operation of the heat exchanger 1, the shell space 3 is filled with a
first
medium Ml. This inlet stream into the heat exchanger 1 is usually two-phase,
but
may also be just liquid. The liquid phase Fl of the first medium M1 then forms
a
bath surrounding the plate heat exchangers 4, 5, the gaseous phase G1 of the
first medium M1 collecting above the liquid phase Fl in an upper region of the
shell space 3, from where it can be drawn off.
The liquid phase Fl of the first medium M1 rises up in the first heat transfer
passages P of the plate heat exchangers 4, 5 and, as a result of indirect heat
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transfer, is thereby partially vaporized by the second medium M2 to be cooled,
which is for example conducted in cross-flow in relation to the first medium
M1 in
the second heat transfer passages P' of the plate heat exchangers 4, 5. The
gaseous phase G1 of the first medium M1 thereby produced can leave at an
upper end of the plate heat exchangers 4, 5 and is drawn off from the shell
space
3 above the blocks 4, 5. Part of the liquid phase Fl continues to circulate in
the
shell space 3, the part referred to being transported from the bottom upward
in the
plate heat exchangers 4, 5 in the first heat transfer passages P and then
flowing
downward again outside the plate heat exchangers 4, 5 in the shell space 3.
The second medium M2 is directed into the plate heat exchangers 4, 5 and,
after
passing through the assigned second heat transfer passages P', is drawn off
from
the plate heat exchangers 4 5 in a cooled or liquefied state.
In order then to still the liquid phase Fl in the shell space 3 when there is
a
fluctuating movement of the shell 2, in which the longitudinal axis or
cylinder axis
fluctuates about the vertical z, according to Figure 1 three units 100 are
provided,
each with a number of parallel channels 10, which respectively extend along a
longitudinal axis L, which runs parallel to the longitudinal axis z of the
shell 2.
According to Figure 2, these channels 10 are preferably formed by a plurality
of
hollow profiles 11, which are suitably connected to one another, delimit for
example circular-cylindrical channels 10 and at the same time have at each of
the
end faces on both sides an opening 10a, 10b, the one opening 10a facing upward
and being located - along the vertical z - approximately at the height of an
upper
end of the respective plate heat exchanger 4, 5 and the other, opposite
opening
10b respectively facing downward and ending - along the vertical z - below the
blocks 4, 5. The channels 10 are preferably arranged next to one another along
two orthogonal spatial directions.
The vertical channels 10 then allow the liquid phase Fl that is leaving the
respective plate heat exchanger 4, 5 at the upper end from the first passages
P to
circulate again to the bottom, where the liquid phase Fl then enters the first
heat
transfer passages P at the lower end of the plate heat exchangers 4, 5 and, on
account of the thermosiphon effect, is drawn upward again, is thereby
partially
vaporized and cools down the second medium M2.
The vertical channels 10 in this case represent a flow resistance in the
horizontal
direction and therefore suppress corresponding horizontal motions of the
liquid
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phase Fl of the first medium Ml, while the vertical circulation referred to
through
the channels 10 is protected.
According to Figure 1, one of the units 100 between the two plate heat
exchangers 4, 5 is arranged laterally in relation to the two blocks 4, 5. The
two
other units 100 are respectively arranged between a plate heat exchanger 4, 5
and a horizontally neighboring portion or inner side region 2a of the
peripheral
walling 14 of the shell 2.
Figure 3 shows a modification of the heat exchanger 1 according to Figure 1,
which as a difference from Figure 1 has a lying, longitudinally extended shell
2,
which extends along a longitudinal axis or cylinder axis that coincides with
the
horizontal, that is to say runs perpendicularly in relation to the vertical z.
As a
difference from Figure 1, here two plate heat exchangers 4, 5 are arranged one
behind the other along the longitudinal axis of the shell 2, the two blocks 4,
5
respectively being flanked laterally on both sides by a unit 100, which is
designed
in the way described above, the units 100 respectively flanking the two blocks
4, 5
over the entire combined length of the two blocks 4, 5 along the longitudinal
axis
of the shell 2.
Figure 4 shows a further modification of the heat exchanger 1 according to
Figure
1, in which, as a difference from Figure 1, the channels 10 run horizontally,
that is
to say perpendicularly in relation to the longitudinal axis of the standing
shell 2,
which coincides with the vertical z. The openings 10a, 10b of the channels 10
then
respectively face in a horizontal direction. According to Figure 1, the units
100 are
arranged with respect to the plate heat exchangers 4, 5, the unit 100 between
the
two blocks 4, 5 having channels 10 with a greater flow cross-sectional area
than
the units 100 on the outer sides of the blocks 4, 5. Along the vertical z, all
of the
units 100 project beyond the upper and lower ends of the plate heat exchangers
4, 5, in order as far as possible to still the entire filling level of the
liquid phase Fl
of the first medium M1 when there is a fluctuating movement of the heat
exchanger 1, in which the longitudinal axis z of the shell 2 according to
Figure 4
changes its inclination, in particular out of the plane of the page. The
stilling is in
this case produced by the flow resistance that the liquid phase Fl undergoes
in
the horizontal channels, for example when flowing back and forth between the
openings 10a, 10b of the channels 10. According to Figure 4, the channels 10
or
units 100 may be formed with a plurality of cross-sectional rectangular or
square
hollow profiles or by plate-shaped elements, in particular sheets (see above),
that
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are fitted one into the other or fastened to one another. According to Figure
5, the
vertical channels 10 may not only be rectangularly formed in cross section, as
shown by way of example in Figure 4, but also circularly. Other forms are
likewise
conceivable. To increase the flow resistance in the horizontal direction,
individual
horizontal channels 10 may be provided with an additional flow retarder (for
example a cross-sectional constriction) 12 or be completely closed 12.
Figure 6 finally shows a heat exchanger 1 in the manner of Figure 4 with
horizontal channels 10, the shell 2 of the heat exchanger now being formed
according to Figure 3 and arranged as lying. In this case, on both sides of
the
plate heat exchangers 4, 5 arranged one behind the other, which are placed
according to Figure 3, provided in each case between the respective block 4, 5
and a horizontally neighboring inner side region or portion of the peripheral
walling
14 of the shell 2 there is a unit 100 with a number of horizontal channels 10
arranged one above the other and next to one another, which however have a
smaller extent along the longitudinal axis of the shell 2 than the blocks 3, 4
along
this direction. This allows the least possible disturbance of the vertical
circulation
of the liquid phase Fl (see above). According to Figure 6, a further unit 100
is also
arranged between the two blocks 4, 5 along the longitudinal axis of the shell
2.
Here, too, the stilling of the liquid phase Fl of the first medium works in
the way
described on the basis of Figure 4.
In principle, the interconnected (or else individual) hollow profiles 11 or
channels
10 may be provided in different cross-sectional forms (for example circular,
rectangular, honeycomb-shaped) and lengths at any position of the shell space
3
not occupied by the respective plate heat exchanger 4, 5, but mainly in the
liquid-
filled region (that is to say next to the block 4 or 5, the blocks 4, 5 and/or
between
the blocks 4, 5). The number of units or registers 100 is adaptable. These
units
100 are only flowed through by the liquid phase Fl in the vertical direction
or in
the horizontal direction. The assembly itself represents a flow resistance in
the
horizontal direction. As a result, horizontal flows are damped. The units 100
or
channels 10 can be adapted to the respective requirements both in vertical
dimensions and in horizontal dimensions and may possibly also be subdivided.
The size of the individual channels 10 in cross section is flexible and can
likewise
be adapted to the respective requirements. The individual channels 10 of the
units
100 may have different lengths. In particular in the case of horizontal
channels 10
or hollow profiles 11, individual profiles 11 may be closed, in order to adapt
the
flow resistance. As a result, horizontal flows are damped.
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To sum up, the units or hollow-profile registers 100 according to the
invention
allow a great influence to be exerted on the flow direction of the circulating
liquid
Fl in the container 2, without a great number of individual parts being
required for
this. The liquid volume outside the plate heat exchangers 4, 5 can be
segmented
to a very great extent, though the production and assembly expenditure for
this
remains relatively low. The segmentation also allows small wall thicknesses of
the
units 100 or channels 10/hollow profiles 11, since the assembly 100 represents
a
robust body 100 and only allows small-scale liquid motions. Adapting the
dimensions of the individual elements 10 and of the assembly 100 as a whole
allows the natural frequencies of oscillating liquid Fl in the container 2 or
shell
space 3 to be influenced and motions to be damped. Consequently, natural
frequency excitation and high oscillation amplitudes can be prevented.
Particularly preferably, the heat exchanger 1 according to the invention is
used on
a floating body on a body of water, for example as a component of a floating
installation for producing liquefied natural gas (LNG).
,
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List of designations
1 Heat exchanger
2 Shell
2a Inner side
3 Shell space
4, 5 Plate heat exchanger
Channel
10a, 10b Opening
11 Hollow profile
14 Walling
Wall
40 Separating plates
41 Heat-directing structures or fins
42 Side bars
100 Unit
M1 First medium
M2 Second medium
G1 Gaseous phase of first medium
Fl Liquid phase of first medium
First heat transfer passage
P' Second heat transfer passage
Vertical
