U.S. patent application number 14/174174 was filed with the patent office on 2014-08-07 for heat exchanger and heat management system having such a heat exchanger.
The applicant listed for this patent is ALBERT VOGERL. Invention is credited to ALBERT VOGERL.
Application Number | 20140216701 14/174174 |
Document ID | / |
Family ID | 50002457 |
Filed Date | 2014-08-07 |
United States Patent
Application |
20140216701 |
Kind Code |
A1 |
VOGERL; ALBERT |
August 7, 2014 |
HEAT EXCHANGER AND HEAT MANAGEMENT SYSTEM HAVING SUCH A HEAT
EXCHANGER
Abstract
A heat exchanger for heat transfer between a heat exchange
medium and a surrounding liquid has first and second main lines.
The first main line defines a main through-flow cross section. A
heat exchanger section carries a heat exchange medium and its
through-flow cross section in larger than the main through-flow
cross section. The heat exchanger section is connected at a first
end to the first main line and at a second end to the second main
line such that the heat exchange medium is distributed
hydraulically symmetrically between the first main line and the
heat exchanger section and between the second main line and the
heat exchanger section. A heat management system has a heat
circuit, a hollow, liquid-filled pile let into the ground, and one
or more heat exchangers in the hollow pile.
Inventors: |
VOGERL; ALBERT; (NEUMARKT,
DE) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
VOGERL; ALBERT |
NEUMARKT |
|
DE |
|
|
Family ID: |
50002457 |
Appl. No.: |
14/174174 |
Filed: |
February 6, 2014 |
Current U.S.
Class: |
165/168 |
Current CPC
Class: |
Y02E 60/142 20130101;
Y02E 60/14 20130101; F28D 15/00 20130101; F28D 20/0052
20130101 |
Class at
Publication: |
165/168 |
International
Class: |
F28D 15/00 20060101
F28D015/00 |
Foreign Application Data
Date |
Code |
Application Number |
Feb 6, 2013 |
DE |
102013001995.8 |
Claims
1. A heat exchanger for heat transfer between a heat exchange
medium and a surrounding liquid, the heat exchanger comprising: a
first main line having a main through-flow cross section; a second
main line; a heat exchanger section for conducting the heat
exchange medium therethrough, said heat exchanger section having a
heat exchanger through-flow cross section greater than the main
through-flow cross section; said heat exchanger section having a
first end connected to said first main line and a second end
connected to said second main line to cause the heat exchange
medium to be distributed substantially hydraulically symmetrically
between said first main line and said heat exchanger section and
between said second main line and said heat exchanger section.
2. The heat exchanger according to claim 1, wherein said second
main line has a through-flow cross section corresponding to the
main through-flow cross section.
3. The heat exchanger according to claim 1, wherein said heat
exchanger section has an elongate shape in a flow direction of the
heat exchange medium.
4. The heat exchanger according to claim 1, wherein said heat
exchanger section has a hollow cylindrical geometry.
5. The heat exchanger according to claim 4, wherein said heat
exchanger section comprises a flow channel which is formed by a
hollow cylindrical slot.
6. The heat exchanger according to claim 4, wherein said heat
exchanger section is formed with a plurality of elongate flow
channels that are arranged symmetrically with respect to one
another along a cylinder shell face.
7. The heat exchanger according to claim 4, wherein said first end
of said heat exchanger section is connected centrally to said first
main line and said second end is connected centrally to said second
main line.
8. The heat exchanger according to claim 7, which comprises a
distributor coupling said first main line to said heat exchanger
section and a distributor coupling said second main line in each
case with a star-shaped coupling.
9. The heat exchanger according to claim 7, wherein said second
main line is guided in a direction of said first end within an area
enclosed by said heat exchanger section.
10. The heat exchanger according to claim 1, wherein said second
main line is thermally insulated with respect to surroundings
thereof.
11. The heat exchanger according to claim 1, wherein a flow
direction of the heat exchange medium in said heat exchanger
section is oriented substantially vertically.
12. A heat management system, comprising: a heat circuit for a heat
exchange medium; at least one hollow pile filled with a liquid and
let into the ground, said hollow pile having a substantially
greater length in comparison with a width thereof, and being
oriented with a longitudinal direction thereof substantially
perpendicularly with respect to the ground surface; at least one
heat exchanger according to claim 1, disposed with the first end of
the heat exchanger section close to the ground surface in said
hollow pile, and connected by way of said first and second main
lines to said heat circuit, and conducting the heat exchange medium
therethrough in order to transfer heat between the liquid and said
heat circuit.
13. The heat management system according to claim 12, wherein said
first main line is selectively usable as a feed line or as a return
line.
14. The heat management system according to claim 13, wherein said
at least one heat exchanger is one of a plurality of heat
exchangers disposed next to one another in said hollow pile.
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] This application claims the priority, under 35 U.S.C.
.sctn.119, of German patent application DE 10 2013 001 995.8, filed
Feb. 6, 2013; the prior application is herewith incorporated by
reference in its entirety.
BACKGROUND OF THE INVENTION
Field of the Invention
[0002] The invention relates to a heat exchanger for the transfer
of heat between a heat exchange medium and a surrounding liquid.
Furthermore, the invention relates to a heat management system
which has a heat exchanger of this type.
[0003] Refrigerating machines are conventionally used for supplying
cooling circuits for machines. The refrigerating machines cool the
heat exchange medium (usually water), which flows in the cooling
circuit, to a desired temperature. One disadvantage of the
refrigerating machines, however, is their high energy
consumption.
[0004] As an energy-saving alternative, the cooling circuits are
partially also cooled in cooling towers via fluid/air heat
exchangers or in direct contact of the fluid with the air. A
limiting factor here for the cooling circuit temperature which can
be achieved is the ambient temperature which is frequently subject
to high fluctuations throughout the year and/or according to the
time of day.
[0005] As an alternative, the cooling circuits are also cooled in
cold liquids, such as groundwater or river water which is stored,
for example, in pools or tanks. For this purpose, different forms
of heat exchangers are known. Typically, tubular heat exchangers
are frequently used which guide the heat exchange medium through
tube bundles which are bent in a U-shape, and which dip into the
liquid of a tank of this type.
SUMMARY OF THE INVENTION
[0006] It is accordingly an object of the invention to provide a
heat exchanger and an associated management system which overcome a
variety of disadvantages of the heretofore-known devices and
methods of this general type and which provides for a heat
exchanger that is of simple construction but is nevertheless
efficient. It is a further object of the invention to provide for a
heat management system which is of simple construction and is
efficient.
[0007] With the foregoing and other objects in view there is
provided, in accordance with the invention, a heat exchanger for
heat transfer between a heat exchange medium and a surrounding
liquid, the heat exchanger comprising:
[0008] a first main line having a main through-flow cross
section;
[0009] a second main line;
[0010] a heat exchanger section for conducting the heat exchange
medium therethrough, the heat exchanger section having a heat
exchanger through-flow cross section greater than the main
through-flow cross section;
[0011] the heat exchanger section having a first end connected to
the first main line and a second end connected to the second main
line to cause the heat exchange medium to be distributed
substantially hydraulically symmetrically between the first main
line and the heat exchanger section and between the second main
line and the heat exchanger section.
[0012] With the above and other objects in view there is also
provided, in accordance with the invention, a heat management
system that comprises:
[0013] a heat circuit for a heat exchange medium;
[0014] at least one hollow pile filled with a liquid and let into
the ground, the hollow pile having a substantially greater length
in comparison with a width thereof, and being oriented with a
longitudinal direction thereof substantially perpendicularly with
respect to the ground surface;
[0015] at least one heat exchanger as summarized above and
described herein; the heat exchanger is disposed with the first end
of the heat exchanger section close to the ground surface in the
hollow pile, and connected by way of the first and second main
lines to the heat circuit, and conducting the heat exchange medium
therethrough in order to transfer heat between the liquid and the
heat circuit.
[0016] In other words, the heat exchanger according to the
invention is provided for the transfer of heat between a heat
exchange medium and a surrounding liquid. According to the
invention, the heat exchanger comprises a first main line and a
second main line in order to guide the heat exchange medium. Here,
the through-flow cross section of the first main line is called the
main through-flow cross section. Furthermore, the heat exchanger
comprises a heat exchanger section, through which the heat exchange
medium can flow. Here, the heat exchanger section has a
through-flow cross section which is called the heat exchanger
through-flow cross section, said heat exchanger through-flow cross
section being enlarged in comparison with the main through-flow
cross section. Moreover, the heat exchanger section is connected at
a first end to the first main line and at a second end to the
second main line in such a way that the heat exchange medium is
divided substantially, that is to say approximately, hydraulically
symmetrically between the first main line and the heat exchanger
section and between the second main line and the heat exchanger
section.
[0017] The term "hydraulically symmetrical distribution" is
understood here and in the following text to mean that the heat
exchange medium is transferred from the first and the second main
line to the heat exchanger section in such a way that the heat
exchange medium flows in every part cross section of the heat
exchanger through-flow cross section, apart from boundary effects,
constantly at an approximately identical flow speed. This
(virtually) homogeneous through-flow of the heat exchanger
through-flow cross section advantageously leads in the heat
exchanger section to a uniform transfer of heat between the heat
exchange medium and the surroundings or the liquid.
[0018] Moreover, the heat exchanger through-flow cross section
which is enlarged in comparison with the main through-flow cross
section advantageously achieves a situation where the heat exchange
medium has a slower flow speed when flowing through the heat
exchanger section in comparison with the flow through the first
main line. This has the advantage that a particularly long dwell
time in the heat exchanger section is available to the heat
exchange medium, which particularly long dwell time results in an
improved exchange of heat. To this end, the heat exchanger
through-flow cross section is preferably considerably greater than
the main through-flow cross section, for example at least twice as
great.
[0019] The heat exchanger section is preferably manufactured from
stainless steel. In the context of the invention, however, the heat
exchanger section can also be manufactured from aluminum or plastic
with an optimized thermal conductivity.
[0020] In one preferred embodiment, the through-flow cross section
of the second main line corresponds to the main through-flow cross
section, that is to say the through-flow cross section of the first
main line. This has the advantage that the flow speed of the heat
exchange medium is identical in the first and in the second main
line.
[0021] In one particularly preferred embodiment, the heat exchanger
section has an elongate shape in the flow direction of the heat
exchange medium. The heat exchanger section is preferably of
considerably longer configuration here than the greatest extent,
perpendicular with respect to the flow direction, of the
cross-sectional area of the heat-exchanger section, through which
cross-sectional area the heat exchange medium flows. For example,
the length is at least three times said extent. In particular, the
heat exchanger section has a length of at least 4 m. The heat
transfer section, formed by the heat exchanger section, for the
heat exchange medium is therefore particularly large, with the
result that a particularly long time for the transfer of heat to
the surroundings or the surrounding liquid is available to the heat
exchange medium during the through-flow of the heat exchanger
section.
[0022] In the context of the invention, it is conceivable in
principle that the heat exchanger section is formed from a flat
tube with a rectangular through-flow cross section or by way of a
plurality of tubes which are arranged next to one another in one
line. In one expedient embodiment, the heat exchanger section has a
hollow cylindrical geometry, however. This is understood to mean
that the heat exchange medium within the heat exchanger section is
guided along a cylinder shell face at a spacing from a central axis
of the heat exchanger section. In other words, the heat exchanger
through-flow cross section lies completely between two concentric
cylinder shell faces. As a result, the heat exchanger section has
at least one contact area (or one contact area section) which is
directed with its surface perpendicular to the outside from the
hollow cylindrical geometry, and at least one further contact area
(or one further contact area section) which is directed with its
surface perpendicular toward the inner side of the hollow
cylindrical geometry. The heat exchange medium which flows in the
heat exchanger section is therefore surrounded both on the outside
and on the inside by the surrounding liquid.
[0023] In one possible embodiment of the invention, the heat
exchanger section has a single flow channel which is formed by a
hollow cylindrical slot as viewed in cross section. In other words,
the heat exchanger section in this embodiment corresponds to a
double-walled tube, the inner and outer tube walls of which form a
hollow cylinder. Each of the tube walls therefore also forms an
outwardly and inwardly, respectively, directed contact area of the
heat exchanger section. In this case, the heat exchange medium
flows in the hollow cylindrical slot, that is to say between the
inner and the outer tube wall. On account of the symmetrical
distribution of the heat exchange medium to the heat exchanger
section, the heat exchange medium flows over the entire annular
cross-sectional area of the hollow cylindrical slot (at least at a
sufficient spacing from the opening points at the upper and lower
end of the heat exchanger section) approximately at a homogeneous
(that is to say, constant in the circumferential direction) flow
speed.
[0024] In one preferred embodiment, however, the heat exchanger
section has a plurality of flow channels which are arranged
distributed symmetrically with respect to one another around the
cylinder shell of the hollow cylindrical geometry. Here, the flow
channels are, in particular, of elongate, that is to say
rectilinear, configuration between the first and the second end of
the heat exchanger section and run in an axially parallel manner.
In the context of the invention, however, the flow channels can
also in principle be set toward the axis of the hollow cylindrical
heat exchanger section, in particular can run in a helical manner.
Here, each of said flow channels forms, with its through-flow cross
section, in each case one of the part cross sections of the heat
exchanger through-flow cross section, in which the heat exchange
medium flows at an identical flow speed.
[0025] In the context of the invention, it is conceivable here to
form the heat exchanger section from two tubes which are made from
corrugated metal and are arranged coaxially with respect to one
another, the corrugation peaks and corrugation troughs of the two
tubes running in the longitudinal direction of the heat exchanger
section. Here, the two "corrugated metal tubes" are dimensioned in
such a way that in each case one corrugation peak of the inner tube
is in contact with one corrugation trough of the outer tube and is
preferably connected to the latter at this point. As a result, each
corrugation trough of the inner tube forms one of the flow channels
with the corrugation peak of the outer tube.
[0026] In a preferable manner and in an embodiment which is
expedient in terms of manufacturing technology, however, the flow
channels are formed by in each case one single tube which runs in
the longitudinal direction of the heat exchanger section. Here, the
tubes are expediently fixed parallel to one another over the length
of the heat exchanger section by at least one spacer element. The
spacer element is formed, for example, by a plate or a ring, on
which the tubes are secured or through which the tubes are
guided.
[0027] On account of the elongate, rectilinear shape of the heat
exchanger section and, in particular, of its flow channels, it is
made possible in a simple way to advantageously utilize a
temperature gradient of the surrounding liquid. Here, in an
analogous manner to the principle of counter flow cooling, the heat
exchange medium is preferably guided through the heat exchanger
section in such a way that the temperature gradient which forms of
the heat exchange medium is directed identically to the temperature
gradient of the surrounding liquid.
[0028] In one expedient embodiment, the heat exchanger section,
and, in particular, its flow channels, are connected at the first
and second end centrally to the first main line and to the second
main line. Here, the first and the second main line are arranged,
in particular, on a center axis or axis of symmetry of the hollow
cylindrical geometry of the heat exchanger section and, from there,
are connected to the heat exchanger section via in each case
identically long connecting channels which are called distributor
channels and in each case have the same through-flow cross
section.
[0029] In one preferred embodiment, the first and the second main
line are coupled via in each case one distributor to the heat
exchanger section in a star-shaped manner. In other words, the
distributor channels extend in the shape of radial beams from the
respective (central) main line in the direction of the or each flow
channel. In one simple embodiment, the distributor is a plate, the
base area of which corresponds to the cross-sectional area of the
heat exchanger section. The first and the second main line are
attached to said plate perpendicularly, that is to say in the
normal direction of the (distributor) plate and are connected to
the distributor channels. Here, the distributor channels are made
in the plate, for example as bores, in particular perpendicularly
with respect to the respective main line, that is to say in the
plate plane, and open into the respective flow channel once again
perpendicularly with respect to the plate plane.
[0030] As an alternative, the (distributor) plate is reduced in
size in comparison with the cross-sectional area of the heat
exchanger section. Here, the respective distributor channels are
extended by way of distributor tubes and are guided out of the
plate. Here, the flow channels are attached via in each case one
angled part to the distributor tubes. The distributor plate is
manufactured, for example, from aluminum.
[0031] In a further alternative embodiment, the distributor is
configured as a spoked wheel. Here, the distributor channels are
guided from the respective main line in the form of tubes radially
to the outside to an annular disk, within which the respective
distributor channel is deflected in the flow direction of the flow
channels. Here, said annular disk expediently additionally serves
as a spacer piece between the distributor channels and optionally
between the tubes which form the flow channels.
[0032] In one preferred and space-saving embodiment, the second
main line is guided in the direction of the first end of the heat
exchanger section within the area which is enclosed by the heat
exchanger section. Here, in particular, the second main line is
guided out of the heat exchanger section between the distributor
channels of the distributor in the region of the first end of the
heat exchanger section.
[0033] In one expedient embodiment, the second main line is
insulated thermally with respect to the surroundings or the liquid
which surrounds the heat exchanger. This effectively prevents that
an interaction of the heat exchange medium which flows in the
second main line takes place with the surroundings or the
surrounding liquid. As a result, for example, the cooled heat
exchange medium can be returned in the liquid, without the heat
exchange medium heating up again in the region of higher liquid
temperatures.
[0034] In the context of the invention, it is conceivable in
principle that the flow direction of the heat exchange medium and
therefore the heat exchanger section itself are oriented
substantially horizontally in the operating state. In this
embodiment, the heat exchanger can be arranged, for example in
order to cool the heat exchange medium, in a river or in a
comparable (flat and horizontally oriented) heat sink. However, the
heat exchanger is preferably used in such a way that the flow
direction and therefore the heat exchanger section are oriented
substantially, that is to say exactly or approximately, vertically.
In this embodiment, the heat exchanger is provided, in particular,
for use in a bore hole which is filled with liquid, for example a
well, a cistern or preferably in an energy pile which is made in
the ground. "Energy pile" is understood to mean a solid pile or a
hollow pile which is filled with liquid and is equipped with a heat
exchanger.
[0035] The heat management system according to the invention
comprises a heat circuit for a heat exchange medium and at least
one hollow pile which is filled with liquid. Here, the hollow pile
is let into the ground and has a substantially greater length in
comparison with its width. In addition, the hollow pile is oriented
with its longitudinal direction substantially, that is to say
exactly or approximately, perpendicularly with respect to the
ground surface. Moreover, the heat management system comprises a
heat exchanger of the type described at the outset, which heat
exchanger is arranged with the first end of its heat exchanger
section close to the ground surface in the hollow pile. That is to
say, the heat exchanger section is arranged with its first end in
the region of an upper end of the hollow pile, the second end of
the heat exchanger section preferably being arranged in the hollow
pile such that it is distant from the ground surface, that is to
say deeper than the first end. Here, the heat exchanger section
preferably reaches with its second end as far as or at least
virtually as far as the lower end of the hollow pile. The heat
exchanger is connected by means of its first and second main line
to the heat circuit and can be flowed through by the heat exchange
medium for the transfer of heat between the liquid and the heat
circuit.
[0036] The liquid, with which the hollow pile is filled,
advantageously makes a particularly effective transfer of heat
between the heat exchange medium and the liquid possible by way of
heat-induced circulation around the heat exchanger section.
Furthermore, the liquid also makes an efficient transfer of heat
possible between the ground which surrounds the hollow pile and the
liquid itself. On account of the pronounced longitudinal extent and
the perpendicular installed position of the hollow pile, an
advantageous temperature stratification is additionally produced
within the liquid in the hollow pile during operation of the heat
management system. As a consequence of said temperature
stratification, greatly different temperature levels within the
liquid are formed at both longitudinal ends of the hollow pile,
that is to say in the region of the upper and lower end. One
advantageous effect of said temperature stratification consists
here in that the low and high temperature levels at the lower and
upper end of the hollow pile remain largely constant even in the
case of an input of heat into the hollow pile via the heat
exchanger, since a virtually mixing-free exchange of heated liquid
volumes with cold liquid takes place within the hollow pile. The
same applies to the removal of heat from the hollow pile.
[0037] In one preferred embodiment, the hollow pile has a length of
at least 5 m, in particular a length of between 20 m and 40 m. A
length of this type assists the formation of the temperature
stratification and the associated temperature stability. In
particular, on account of the great length of the hollow pile and
the corresponding installation depth into the ground, the
temperature stratification is already produced inherently by way of
the exchange of heat of the liquid in the hollow pile with the
surrounding ground, which leads to an equalization of the local
liquid temperature to the natural temperature profile of the
ground.
[0038] It is utilized here for cooling purposes that the ground as
a rule has an at least approximately constant temperature which is
therefore independent of the season below a depth of approximately
10 m. This temperature is typically approximately 8.degree. C. in
moderate climate zones. Here, the exchange of heat with the
surrounding ground extends the capacity of the hollow pile to store
heat output by the liquid and makes rapid energetic regeneration of
the hollow pile possible after an extensive input of heat or
removal of heat.
[0039] In one preferred embodiment, the hollow pile is formed, in
particular, by a reinforced concrete pipe which is closed in a
liquid-tight manner at the intended lower end and which is closed
by way of a cover at its upper end in the installed state.
[0040] In one expedient embodiment, the length of the heat
exchanger section corresponds approximately to the length of the
hollow pile or undershoots the latter slightly, with the result
that the heat exchanger section can be arranged completely within
the hollow pile.
[0041] On account of the stable temperature stratification in the
hollow pile, it is possible, moreover, to use the hollow pile both
as a heat sink for cooling purposes and as a heat source for
heating. For this purpose, the first main line of the heat
exchanger can be used as feed line or return line. Here, the heat
exchanger is operated for cooling the heat exchange medium in such
a way that the heat exchange medium is introduced via the first
main line into the heat exchanger section and is guided back via
the second main line at the second end of the heat exchanger
section. The heat exchange medium therefore flows through the
liquid column of the hollow pile from top to bottom and is cooled
increasingly in the process on account of the above-described
temperature stratification in the hollow pile as a result of the
decreasing temperature of the liquid in the hollow pile. Here, as
high an equalization as possible of the temperature of the heat
exchange medium to the respective temperature level of the liquid
in the hollow pile is achieved by way of suitable dimensioning of
the heat exchanger through-flow cross section and the particularly
slow flow speed of the heat exchange medium which is achieved as a
result. When the second end of the heat exchanger section is
reached, the heat exchange medium is fed via the distributor to the
second main line and is guided back to the heat circuit. On account
of the optionally present thermal insulation of the second main
line, the heat exchange medium cannot warm up again in the region
of the warmer temperature layers when flowing through the hollow
pile from the bottom to the top.
[0042] For the reverse case, namely that the heat exchange medium
is to be warmed up in comparison with the temperature which is
present in the heat circuit, in one expedient embodiment the
comparatively cold heat exchange medium is guided via the
(optionally thermally insulated) second main line into the lower
end of the hollow pile and is guided there into the second end of
the heat exchanger section. From there, the heat exchange medium
rises in the flow channel or flow channels in the direction of the
first end of the heat exchanger section and is heated in the
process via the transfer of heat from the increasingly warm liquid
layers in the hollow pile. When the first end of the heat exchanger
section is reached, the heat exchange medium which is then heated
is guided via the first main line back into the heat circuit. In
the context of the invention, the first main line can additionally
likewise be thermally insulated.
[0043] The first heat circuit and the heat exchanger which is
connected to it preferably form a closed system. For example, a
heat source or a heat sink which is assigned to a consumer, in
particular a machine which is to be cooled or
temperature-controlled or, as an alternative, a building heating or
cooling system, can be connected to said closed system.
[0044] In a further embodiment of the heat management system, a
plurality of the above-described heat exchangers are arranged next
to one another in the hollow pile. Depending on the cross-sectional
profile of the hollow pile (polygonal or circular), the heat
exchangers are arranged here in a lattice-shaped or in a circular
structure in the hollow pile. In one embodiment which is expedient
in terms of manufacturing technology, the hollow pile has, in
particular, a circular cross-sectional profile. In this case, the
heat exchangers are preferably arranged in the hollow pile in a
comparable manner to rounds in a cylinder of a revolver. Here, in
the context of the invention, one of the heat exchangers can also
be arranged on the "rotational axis of the cylinder," that is to
say the center axis of the hollow pile.
[0045] Other features which are considered as characteristic for
the invention are set forth in the appended claims.
[0046] Although the invention is illustrated and described herein
as embodied in a heat exchanger and heat management system having a
heat exchanger of this type, it is nevertheless not intended to be
limited to the details shown, since various modifications and
structural changes may be made therein without departing from the
spirit of the invention and within the scope and range of
equivalents of the claims.
[0047] The construction and method of operation of the invention,
however, together with additional objects and advantages thereof
will be best understood from the following description of specific
embodiments when read in connection with the accompanying
drawings.
BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING
[0048] FIG. 1 shows a diagrammatic side view of a heat
exchanger;
[0049] FIG. 2 shows an enlarged illustration with interruptions of
the heat exchanger according to FIG. 1;
[0050] FIG. 3 shows the heat exchanger according to FIG. 1 in a
section III-III according to FIG. 2;
[0051] FIG. 4 shows the heat exchanger according to FIG. 1 in a
section IV-IV according to FIG. 2;
[0052] FIG. 5 shows a diagrammatic side view of a heat management
system having a hollow pile which is arranged in the ground and a
heat exchanger according to FIG. 1 which is arranged in said hollow
pile;
[0053] FIG. 6 shows an alternative exemplary embodiment of the heat
exchanger in a view according to FIG. 2;
[0054] FIG. 7 shows the heat exchanger according to FIG. 6 in a
section VII-VII;
[0055] FIGS. 8 and 9 show two further alternative exemplary
embodiments of the heat exchanger in an illustration according to
FIG. 7; and
[0056] FIG. 10 shows the heat exchanger according to FIG. 9 in a
view according to FIG. 2.
DETAILED DESCRIPTION OF THE INVENTION
[0057] Referring now to the figures of the drawing in detail and
first, particularly, to FIGS. 1 and 2 thereof, there is shown a
heat exchanger 1 which is provided for the transfer of heat between
a heat exchange medium and a liquid 2 which surrounds the heat
exchanger. The heat exchanger 1 comprises a first main line 3 and a
second main line 4. Furthermore, the heat exchanger 1 comprises a
heat exchanger section 5, through which the heat exchange medium
can flow. The heat exchanger section 5 is connected at a first end
6 to the first main line 3 and at a second end 8 which lies
opposite the first end 6 in the longitudinal direction 7 to the
second main line 4.
[0058] Here, the first main line 3 has a main through-flow cross
section D. While the delimiting arrows in the figures point to the
outer diameter of the pipes, it will be understood that the
diameter is the inner diameter and the corresponding cross-section
D is the inner cross-section, the area that is open to the flow.
Here, the through-flow cross section of the second main line 4
corresponds to the main through-flow cross section D. The heat
exchanger section 5 is formed from eight tubes 9 which in each case
form a flow channel for the heat exchange medium and run
rectilinearly in the longitudinal direction 7 between the first end
6 and the second end 8 of the heat exchanger section 5. Here, the
flow direction of the tubes 9 corresponds to the longitudinal
direction 7. Moreover, the individual tube cross sections D.sub.R
are dimensioned in such a way that the sum of all tube cross
sections D.sub.R exceeds the main through-flow cross section D of
the first and second main line 3, 4 considerably, for example by
two times. As a result, the flow speed of the heat exchange medium
in the heat exchanger section 5 is reduced in comparison with the
main lines 3, 4.
[0059] At the first end 6 of the heat exchanger section 5, its
tubes 9 are connected via a distributor, called the first
distributor plate 10, or head plate 10, in the following text, to
the first main line 3. At the second end 8, the tubes 9 are
connected via a second distributor plate 11, or foot plate 11, to
the second main line 4. As can be seen from FIGS. 3 and 4, the
eight tubes 9 are arranged here in a circular ring shape on the
distributor plates 10 and 11, with the result that the heat
exchanger section 5 has a hollow cylindrical geometry. That is to
say, the heat exchanger section 5 borders a virtually circular area
section with its tubes 9.
[0060] The first main line 3 is placed onto the distributor plate
10 centrally with respect to the tubes 9 that is to say on a center
axis of said (circular) distributor plate 10. The tubes 9 are
connected to the first main line 3 via in each case equally long
distributor channels 12 which have the same cross section and are
made in each case as a bore radially in the distributor plate 10.
Furthermore, the tubes 9 protrude perpendicularly in the
longitudinal direction 7 from that side of the distributor plate 10
which lies opposite the first main line 3. The second main line 4
is connected in a corresponding way via the connecting plate 11 to
the tubes 9 (see FIG. 4). In contrast to the first connecting plate
10, however, the second main line 4 is guided out of the connecting
plate 11 on the same side as the tubes 9. As can also be seen from
FIGS. 1 and 2, the second main line 4 is thus guided from the
second end 8 in the direction of the first end 6 in the area
section which is bordered by the tubes 9, that is to say within the
heat exchanger section 5. Here, the second main line is guided
through the first distributor plate 10 in the region of the first
end 6 between the distributor channels 12 (see FIGS. 1 to 3).
[0061] The distribution of the heat exchange medium between the
first or the second main line 3 or 4 and the tubes 9 takes place in
a hydraulically symmetrical manner via the distributor plates 10 or
11, insofar as the heat exchange medium in each of the tubes 9
flows under the same flow conditions, that is to say with an
identical flow speed, on account of the distributor channels 12
which are in each case homogeneous.
[0062] As can be seen from FIGS. 1 to 4, the second main line 4 is
insulated thermally with respect to the liquid 2 by an insulating
jacket 14.
[0063] The heat exchanger section 5 has a length L which is
considerably greater than the width of the through-flow cross
section of the heat exchanger section 5, that is to say greater
than the sum of the tube cross sections DR. The length L of the
heat exchanger section 5 is additionally also considerably greater
than the (overall) diameter of the hollow cylindrical heat
exchanger section 5. Here, the length L of the heat exchanger
section 5 is at least 4 m, in an expedient dimensioning between 20
m and 40 m. In order to stabilize the tubes 9 and their parallel
arrangement over the length L, the heat exchanger section 5 has two
spacer elements 16 between the first end 6 and the second end 8.
The spacer elements 16 are configured as plates, through which the
tubes 9 and the second main line 4 are guided (shown by dashed
lines, see FIG. 2).
[0064] FIG. 5 shows the heat exchanger 1 in the case of use in a
heat management system 18. Here, the heat management system 18
comprises a heat circuit (not shown in greater detail) which feeds
the heat exchange medium via the first main line 3 or the second
main line 4 into the heat exchanger 1 or the heat exchanger section
5 and removes it from the heat exchanger section 5. Furthermore,
the heat management system 18 comprises a hollow pile 22 which is
let perpendicularly into the ground 20 and is filled with the
liquid 2. The heat exchanger 1 is arranged within the hollow pile
22 in such a way that the heat exchanger section 5 is surrounded
completely by the liquid 2. The length L of the heat exchanger
section 5 corresponds approximately to the length of the hollow
pile 22, with the result that the first end 6 of the heat exchanger
section 5 is arranged in the region of the upper end 24 of the
hollow pile 22 and the second end 8 of the heat exchanger section 5
reaches as far as the lower end 26 of the hollow pile 22.
[0065] The hollow pile 22 is closed in a liquid-tight manner at its
lower end 26 by way of a closure plate 28. In the intended
installed state which is shown in FIG. 5, the upper end 24 of the
hollow pile 22 is closed by way of a cover 30, the first and second
main line 3, 4 of the heat exchanger 1 being guided through the
cover 30. In order to make a particularly satisfactory transfer of
heat to the soil 32 possible, the hollow pile 22 is pressed with a
grouting compound 34 in the soil 32.
[0066] Depending on whether the heat exchange medium is to be
cooled or to be heated via the heat exchanger 1, the first and the
second main line 3, 4 can be used both as a feed line and as a
return line. For the case where the heat exchange medium is to be
cooled, it is introduced via the first main line 3 into the first
end 6 of the heat exchanger section 5 and therefore flows in the
direction of the lower end 26 of the hollow pile 22. The result of
the perpendicular installation of the hollow pile 22 is a
temperature stratification in the liquid 2 which becomes cooler
from top to bottom. This leads to the heat exchange medium being
cooled increasingly during the through-flow of the heat exchanger
section 5 from top to bottom. After the converging of the heat
exchange medium via the distributor plate 11 into the main line 4,
the insulating jacket 14 prevents the heat exchange medium which
rises in the direction of the upper end 24 being warmed in the
second main line 4 by interaction with the liquid 2. For the case
where a cool heat exchange medium is to be heated via the heat
management system 18, the heat exchange medium is introduced via
the second main line 4 at the lower (cool) end 26 of the hollow
pile 22 into the heat exchanger section 5. During rising through
the tubes 9 in the direction of the upper (warm) end 24 of the
hollow pile 22, the heat exchange medium heats up and is removed
via the distributor plate 10 and the first main line 3. The
suitability of the first and second main lines 3 and 4 as feed line
and return line is indicated by the flow direction arrows 36.
[0067] FIG. 6 and FIG. 7 show an alternative exemplary embodiment
of the heat exchanger 1. Here, in contrast to the heat exchanger 1
which is shown in FIGS. 1 to 5, the distributor plates 10 and 11 in
each case have a smaller diameter compared to the area section
which is bordered by the tubes 9. The tubes 9 are connected via in
each case one angled part 38 to the distributor channels 12 of the
distributor plates 10 and 11. Here, the angled parts 38 are guided
out of the distributor plates 10 and 11 perpendicularly with
respect to the longitudinal direction 7 and in an extension of the
respective distributor channel 12. The second main line 4 can be
fixed on the first distributor plate 10 in a way which is not shown
in greater detail, for example by way of a pipe clamp.
[0068] In an alternative exemplary embodiment of the heat exchanger
1 according to FIG. 8, the heat exchanger section 5 is formed by a
single double-walled tube 40. Here, the heat exchange medium flows
in an intermediate space (called a hollow cylindrical slot) between
the outer tube wall 41 and the inner tube wall 42 of the
double-walled tube 40. Here, the cross-sectional area of the hollow
cylindrical slot is greater than the cross-sectional area or the
main through-flow cross section D of the first and second main line
3, 4. This therefore likewise results, in the heat exchanger
section 5, in the flow speed of the heat exchange medium which is
slower than in the first and second main lines 3, 4.
[0069] In order to distribute the heat exchange medium from the
first main line 3 to the double-walled tube 40, the first main line
3 is connected to the double-walled tube 40 in a star-shaped manner
via eight distributor tubes 44. The attachment of the second main
line 4 at the second end 8 of the heat exchanger section 5 or the
double-walled tube 40 takes place in an analogous manner. In this
exemplary embodiment, the distribution of the heat exchange medium
to the heat exchanger section 5 also takes place in a hydraulically
symmetrical manner, insofar as the heat exchange medium flows
within the hollow cylindrical slot with a constant flow speed in
the circumferential direction at a sufficient spacing from the
opening points of the distributor tubes 44.
[0070] In a further alternative exemplary embodiment according to
FIG. 9, the heat exchanger section 5 is formed by a double-walled
tube, which is called a corrugated metal tube 46 in the following
text. Here, the inner tube wall 42 is connected to the outer tube
wall 41 at eight connecting points 48. This results in a total of
eight flow channels 50 which run in the longitudinal direction 7
between in each case two connecting points 48, into which flow
channels 50 the main lines 3 and 4 are coupled in a hydraulically
symmetrical manner by means of the distributor tubes 44. The sum of
the individual through-flow cross sections of the flow channels 50
once again exceeds the main through-flow cross section D of the
first and second main line 3, 4.
[0071] As can be gathered from FIG. 10, apertures 52 are made in
the corrugated metal tube 46 within the (elongate) connecting
points 48. The apertures 52 serve, for example, to fasten the heat
exchanger section 5 in the hollow pile 22 which is shown in FIG. 5
and/or to make an exchange of the liquid 2 possible between the
inner side and the outer side of the hollow cylindrical geometry of
the heat exchanger section 5.
[0072] The heat exchanger section 5, in particular the tubes 9, the
double-walled tube 40 and the corrugated metal tube 46, are
manufactured, for example, from stainless steel which is rust-proof
and resistant to salt water. As an alternative, however, the heat
exchanger section 5 can also be manufactured, for example, from
comparatively resistant plastic having a high thermal conductivity.
The distributor plates 10 and 11 and the spacer elements 16 are
manufactured, for example, from aluminum which is resistant to salt
water.
[0073] The subject matter of the invention is not restricted to the
above-described exemplary embodiments. Rather, further embodiments
of the invention can be derived from the above description by a
person skilled in the art. In particular, the individual features
of the invention which are described using the various exemplary
embodiments and the design variants thereof can also be combined
with one another in a different way.
[0074] The following is a summary list of reference numerals and
the corresponding structure used in the above description of the
invention: [0075] 1 Heat exchanger [0076] 2 Liquid [0077] 3 First
main line [0078] 4 Second main line [0079] 5 Heat exchanger section
[0080] 6 First end [0081] 7 Longitudinal direction [0082] 8 Second
end [0083] 9 Tube [0084] 10 Distributor plate [0085] 11 Distributor
plate [0086] 12 Distributor channel [0087] 14 Insulating jacket
[0088] 16 Spacer element [0089] 18 Heat management system [0090] 20
Ground [0091] 22 Hollow pile [0092] 24 Upper end [0093] 26 Lower
end [0094] 28 Closure plate [0095] 30 Cover [0096] 32 Soil [0097]
34 Grouting compound [0098] 36 Flow direction arrow [0099] 38
Angled part [0100] 40 Tube [0101] 41 Outer tube wall [0102] 42
Inner tube wall [0103] 44 Distributor tube [0104] 46 Corrugated
metal tube [0105] 48 Connecting point [0106] 50 Flow channel [0107]
52 Aperture [0108] D Main through-flow cross section (inner
diameter) [0109] D.sub.R Tube cross section [0110] L Length
* * * * *