U.S. patent application number 12/808119 was filed with the patent office on 2010-11-11 for modular heat exchange system.
This patent application is currently assigned to A-HEAT ALLIED HEAT EXCHANGE TECHNOLOGY AG. Invention is credited to Franz Summerer.
Application Number | 20100282439 12/808119 |
Document ID | / |
Family ID | 39591258 |
Filed Date | 2010-11-11 |
United States Patent
Application |
20100282439 |
Kind Code |
A1 |
Summerer; Franz |
November 11, 2010 |
Modular heat exchange system
Abstract
The invention relates to a modular heat exchange system (1)
having a heat exchange module (2, 21, 22) which includes a first
heat exchange module (21) with a heat exchanger (3). In this
respect, an outer boundary of the heat exchange module (2) is
formed by an inflow surface (4) and an outflow surface (5) such
that, for the exchange of heat between a transport fluid (6) and a
heat agent (7) flowing through the heat exchanger (3) in the
operating state, the transport fluid (6) can be supplied to the
heat exchange module (2) via the inflow surface (4), can be brought
into flow contact with the heat exchanger (3) and can be led away
again the heat exchange module (2) via the outflow surface (5). In
accordance with the invention, a first boundary surface (81) of the
first heat exchange module (2, 21) is inclined at a presettable
angle of inclination (.alpha.) with respect to a second boundary
surface (82) of the first heat exchange module (2, 21).
Inventors: |
Summerer; Franz;
(Kottgeisering, DE) |
Correspondence
Address: |
TOWNSEND AND TOWNSEND AND CREW, LLP
TWO EMBARCADERO CENTER, EIGHTH FLOOR
SAN FRANCISCO
CA
94111-3834
US
|
Assignee: |
A-HEAT ALLIED HEAT EXCHANGE
TECHNOLOGY AG
Muenchen
DE
|
Family ID: |
39591258 |
Appl. No.: |
12/808119 |
Filed: |
October 16, 2008 |
PCT Filed: |
October 16, 2008 |
PCT NO: |
PCT/EP08/63991 |
371 Date: |
June 14, 2010 |
Current U.S.
Class: |
165/95 ;
165/104.19 |
Current CPC
Class: |
F28F 1/022 20130101;
F28F 27/02 20130101; F28G 2015/006 20130101; F28D 1/024 20130101;
F28F 21/083 20130101; F28F 21/084 20130101; F28F 1/24 20130101;
F28B 9/08 20130101; F28B 1/06 20130101; F28G 1/08 20130101; F28B
11/00 20130101; F28G 13/00 20130101; F28B 7/00 20130101; F28G 9/00
20130101 |
Class at
Publication: |
165/95 ;
165/104.19 |
International
Class: |
F28G 1/00 20060101
F28G001/00; F28D 15/00 20060101 F28D015/00 |
Foreign Application Data
Date |
Code |
Application Number |
Dec 18, 2007 |
EP |
07123497.5 |
Claims
1. A modular heat exchange system having a heat exchange module (2,
21, 22) including at least one first heat exchange module (21) with
a heat exchanger (3), wherein an outer boundary of the heat
exchange module (2) is formed by an inflow surface (4) and an
outflow surface (5) such that, for the exchange of heat between a
transport fluid (6) and a heat transfer agent (7) flowing through
the heat exchanger (3) in the operating state, the transport fluid
(6) can be supplied to the heat exchange module (2) via the inflow
surface (4), can be brought into flow contact with the heat
exchanger (3) and can be led away again from the heat exchange
module (2) via the outflow surface (5), characterized in that a
first boundary surface (81) of the first heat exchange module (2,
21) is inclined at a presettable angle of inclination (.alpha.)
with respect to a second boundary surface (82) of the first heat
exchange module (2, 21).
2. A heat exchange system in accordance with claim 1, wherein the
first boundary surface (81) of the first heat exchange module (2,
21) is inclined at the presettable angle of inclination (.alpha.)
with respect to the second boundary surface (82) of the first heat
exchange module (2, 21) such that the modular heat exchange system
can be expanded by a second heat exchange module (22), in
particular in compact construction shape, with the second heat
exchange module (22) preferably being identical to the first heat
exchange module (21).
3. A heat exchange system in accordance with claim 1, wherein the
heat exchanger (3) has a supporting function in the forming of the
heat exchange module (2, 21, 22).
4. A heat exchange system in accordance with claim 1, wherein the
heat exchange system is formed from a plurality of heat exchange
modules (2, 21, 22).
5. The heat exchange system in accordance with claim 1, wherein the
angle of inclination (.alpha.) between the first boundary surface
(81) and the second boundary surface (82) of the heat exchange
module (2, 21, 22) is between 0.degree. and 180.degree.,
specifically between 20.degree. and 70.degree., preferably between
40.degree. and 50.degree., and particularly preferably amounts to
45.degree. and/or the angle of inclination (.alpha.) is between
90.degree. and 180.degree., in particular at 120.degree..
6. A heat exchange system in accordance with claim 1, wherein the
angle of inclination (.alpha.) between the first boundary surface
(81) and the second boundary surface (82) of the heat exchange
module (2, 21, 22) has a value of 360.degree./n for the formation
of a heat exchange cluster (1) and the heat exchange cluster (1) is
preferably formed from a number of n identical heat exchange
modules (2, 21, 22), with the angle of inclination (.alpha.)
between the first boundary surface (81) and the second boundary
surface (82) of the heat exchange module (2, 21, 22) preferably
being 60.degree. for the formation of a hexagonal heat exchange
cluster (1) and with the hexagonal heat exchange cluster (1)
preferably being formed from six identical heat exchange modules
(2, 21, 22).
7. A heat exchange system in accordance with claim 1, wherein a
boundary surface (83) of the heat exchange system is formed by a
wall (800) of an installation object, in particular by a wall (800)
of a building.
8. A heat exchange system in accordance with claim 1, wherein a
cooling device (9) is provided for the cooling of the heat
exchanger (3), in particular a fan (9) for the generation of a gas
flow (61), to increase a heat transfer rate between the heat
transfer agent (7) and the transport fluid (6); and/or wherein the
heat exchange system is made as a hybrid system (1) and a
sprinkling device is provided for the sprinkling of the heat
exchanger (3) with a cooling fluid, in particular with cooling
water, and/or a drop separator is provided for the separation of
the cooling fluid.
9. A heat exchange system in accordance with claim 1, wherein the
heat exchanger (3) is formed by a plurality of microchannels (10)
as a microchannel heat exchanger (3); and/or wherein the heat
exchanger (3) is made as a fin heat exchanger (3) with cooling fins
and/or the heat exchange system is made as a combination heat
exchange system (1) of the finned heat exchanger (3) and the
microchannel heat exchanger (3).
10. A heat exchange system in accordance with claim 1, wherein a
sealing is provided, in particular an air sealing (11), for the
regulation of a flowthrough rate of the transport medium (6).
11. A heat exchange system in accordance with any one of the
preceding claims claim 1, wherein a compensation means is provided
for the compensation of thermomechanical strains; and/or wherein a
universal connection element (13) is provided for the connection of
a component of the heat exchange system.
12. A heat exchange system in accordance with claim 1, wherein a
cleaning system (12, 121, 122) is provided specifically including a
dust capturing grid (121) and/or a scraper (121) and/or a washing
device (121), in particular a cleaning opening (121) and/or a
cleaning flap (121); and/or wherein the heat exchanger (3) is
provided at the cleaning flap (121); and/or the heat exchanger (3)
is made as a cleaning flap (121).
13. A heat exchange system in accordance with claim 1, wherein a
control unit, in particular a control unit with a data processing
system for the control of the cooling device (9) and/or of the
cleaning system and/or of the air sealing (11) and/or of an
operating or state parameter of the heat transfer agent (6) and/or
of another operating parameter of the heat exchange system is/are
provided for the control and/or regulation of the heat exchange
system in the operating state.
14. A heat exchange system in accordance with claim 1, wherein the
heat exchange module (2, 21, 22) and/or the heat exchanger (3)
and/or a boundary surface (2, 21, 22) of the heat exchange module
(2, 21, 22), specifically the whole heat exchange system (2, 21,
22), is/are made of a metal and/or of a metal alloy, in particular
of a single metal or of a single metal alloy, in particular of
stainless steel, specifically of aluminum or of an aluminum alloy
with a sacrificial metal preferably being provided as corrosion
protection and/or with the heat exchange system (2, 22, 22) being
provided at least partly with a protection layer, in particular
with a corrosion protection layer.
15. A heat exchange system in accordance with claim 1, wherein the
heat exchange system is a radiator, in particular a radiator for a
vehicle, specifically for a land vehicle, for an aircraft or for a
water vehicle, or is a cooler, a capacitor or an evaporator for a
mobile or stationary heating system, a cooling system or an
air-conditioning system, in particular a cooler apparatus for a
machine, for a data processing system or for a building.
Description
[0001] The invention relates to a heat exchange system in
accordance with the preamble of independent claim 1.
[0002] The use of heat exchange systems is known in a number of
applications from the prior art which can practically not be
overseen. Heat exchangers are used in refrigeration systems such as
in common domestic refrigerators, in air-conditioning systems for
buildings or in vehicles of all kinds, in particular in motor
vehicles, aircraft and ships, as water coolers or as oil coolers in
combustion engines, as condensers or evaporators in refrigerant
circuits and in further innumerable different applications which
are all well-known to the person of ordinary skill in the art.
[0003] In this respect, there are different possibilities of
sensibly classifying the heat exchangers from very different
applications. One attempt is to carry out a distinguishing by the
structure or by the manufacture of the different types of heat
exchangers.
[0004] A division can thus be made in accordance with so-called
"fin heat exchangers", on the one hand, and "minichannel" or
"microchannel" heat exchangers, on the other hand.
[0005] The fin heat exchangers which have been well-known for a
very long time serve, like all types of heat exchangers, for the
transfer of heat between two media, e.g., but not only, for the
transfer from a cooling medium to air or vice versa, such as is
known, for example, from a classical domestic refrigerator in which
heat is emitted to ambient air via the heat exchanger for the
production of a cooling capacity in the interior of the
refrigerator.
[0006] The ambient medium outside the heat exchanger, that is e.g.
water, oil or frequently simply the ambient air, which takes up the
heat, for example, or from which heat is transferred to the heat
exchanger, is either cooled or heated accordingly in this process.
The second medium can e.g. be a liquid cold carrier or heat carrier
or an evaporating or condensing refrigerant. In any case, the
ambient medium, that is e.g. the air, has a substantially lower
heat transfer coefficient than the second medium, that is e.g. the
refrigerant, which circulates in the heat exchanger system. This is
balanced by highly different heat transfer surfaces for the two
media. The medium with the high heat transfer coefficient flows in
the pipe which has a very enlarged surface at the outer side at
which the heat transfer e.g. to the air takes place by thin metal
sheets (ribs, fins).
[0007] FIG. 3 shows a simple example of an element of such a fin
heat exchanger which is known per se. In practice, the heat
exchanger is formed in this respect by a plurality of such elements
in accordance with FIG. 3.
[0008] The ratio of the outer surface to the inner surface depends
in this respect on the fin geometry (=pipe diameter, pipe
arrangement and pipe spacing) as well as on the fin spacing. The
fin spacing is selected differently for different applications.
However, it should be as small as possible from a purely
thermodynamic aspect, but not so small that the pressure loss on
the air side is too large. An efficient optimum is at approximately
2 mm, which is a typical value for the condenser and the heat
exchanger.
[0009] The manufacture of these so-called fin heat exchangers takes
place in accordance with a standardized process known for a long
time. The fins are stamped using a press and a special tool and are
placed in packets with one another. Subsequently, the pipes are
pushed in and expanded either mechanically or hydraulically so that
a very good contact, and thus a good heat transfer, arises between
the pipe and the fin. The individual pipes are then connected to
one another, often soldered to one another, by bends and inlet
tanks and outlet tanks.
[0010] The efficiency is in this respect substantively determined
by the fact that the heat which is transferred between the fin
surface and the air has to be transferred to the pipe via heat
conduction through the fins. This heat transfer is the more
effective, the higher the conductivity or the thickness of the fin
is, but also the smaller the spacing between the pipes is. One
speaks of fin efficiency here. Aluminum is therefore primarily used
as the fin material today which has a high heat conductivity
(approx. 220 W/mK) at economic conditions. The pipe spacing should
be as small as possible; however, this results in the problem that
many pipes are needed. Many pipes mean high costs since the pipes
(made from copper as rule) are much more expensive than the thin
aluminum fins. These material costs could be reduced in that the
pipe diameter and the wall thickness are reduced, i.e. a heat
exchanger is made with a number of small pipes instead of with a
few larger pipes. This solution would be ideal thermodynamically:
Very many pipes at small distances with small diameters. A
substantial cost factor is, however, also the labor time for the
widening and soldering of the pipes. It would increase extremely
with such a geometry.
[0011] A new class of heat exchangers, so-called minichannel or
also microchannel heat exchangers, was therefore already developed
some years ago which are manufactured using a completely different
process and almost correspond to the ideal of a fin heat exchanger:
many small pipes at small intervals.
[0012] Instead of small pipes, however, extruded aluminum sections
are used in the minichannel heat exchanger which have very small
channels with a diameter of e.g. approximately 1 mm. Such an
extruded section likewise known per se is shown schematically e.g.
in FIG. 2. In practice in this respect, a heat exchanger can
already manage, depending on the required heat capacity, with one
single extruded section as a central heat exchange element. To be
able to achieve higher heat transfer capacities, a plurality of
extruded sections can naturally also be provided simultaneously in
one single heat exchanger which are connected to one another, e.g.
soldered to one another, in suitable combinations, for example via
inlet feeds and outlet feeds.
[0013] Such sections can e.g. be manufactured in suitable extrusion
processes simply and in a variety of shapes from a plurality of
materials. However, other manufacturing processes are also known
for the manufacture of minichannel heat exchangers such as the
assembly of suitably shaped sectional metal sheets or other
suitable processes.
[0014] These sections cannot, and also do not have to, be widened
and they are also not pushed into stamped fin packets. Instead, for
example, sheet metal strips, in particular aluminum strips, are
placed between two sections disposed close to one another (common
spacings, for example, <1 cm) so that a heat exchanger packet
arises by alternating placing of sheet metal strips and sections
next to one another. This packet is then soldered completely in a
soldering furnace.
[0015] A heat exchanger having a very high fin efficiency and a
very small filling volume (inner channel side) arises due to the
narrow spacings and the small channel diameters. The further
advantages of this technique are the avoidance of material pairings
(corrosion), the low weight (no copper), the high pressure
stability (approx. 100 bar) as well as the compact construction
shape (typical depth of a heat exchanger e.g. 20 mm).
[0016] Minichannel heat exchangers became established in mobile use
in the course of the 1990s. The low weight, the small block depth
as well as the restricted dimensions required here are the ideal
conditions for this. Automotive radiators as well as condensers and
evaporators for automotive air-conditioning systems are today
realized almost exclusively with minichannel heat exchangers.
[0017] In the stationary area, larger heat exchangers are usually
needed, on the one hand; on the other hand, the emphasis here is
less on the weight and the compact design and more on the ideal
price-performance ratio. Minichannel heat exchangers were
previously too limited in dimensions to be considered for this
purpose. Many small modules would have had to be connected to one
another in a complex and/or expensive manner. In addition, the use
of aluminum is relatively high in the extruded sections so that a
cost advantage was also practically not to be expected from the
material use aspect.
[0018] Due to the high volumes in the automotive sector, the
manufacturing processes for minichannel heat exchangers have become
standardized and have improved so that this technology can today be
called mature. The soldering furnace size has also increased in the
meantime so that heat exchangers can already be produced in the
size of approximately 1.times.2 m.
[0019] The initial difficulties with the connection system have
been remedied. In the meantime, there are a plurality of patented
processes on how the inlet tanks and outlet tanks can be soldered
in.
[0020] However, above all the price of copper, which has increased
greatly with respect to aluminum, has had the result that this
technology is also becoming very interesting for stationary
use.
[0021] In addition to the simple systems in which substantially
only one ambient medium, such as air, is available to the heat
exchanger for the exchange of heat, so-called hybrid coolers or
hybrid dry coolers are known such as are e.g. disclosed in
WO90/15299 or in EP 428 647 B1, in which the gaseous or liquid
medium of the primary cooling circuit to be cooled flows through a
fin heat exchanger and which output the heat to be dissipated via
the cooling fins to the air flow partly as sensitive heat and
partly as latent heat. One or more fans convey the air flow through
the heat exchanger and advantageously have variable speeds. The
dissipation of the latent heat takes place by a liquid medium,
preferably water, which is matched by its specific values such as
conductivity, hardness, carbonate content and is in each case added
to the heat transfer surface on the air side as a drop-forming
liquid film. The excess water drips into a collection bowl directly
beneath the heat exchanger elements. Sprayed heat exchanger
concepts are also known where water is sprayed onto the fin heat
exchanger and evaporates completely and in this process the
evaporation energy is used for the improvement of the heat transfer
as in the wetting for energetic optimization. It is also possible
to work without a water excess here, but a formation of deposits
has to be prevented, for which purposes e.g. VE water is used.
[0022] It is understood that other cooling fluids such as oil can
also be considered in addition to water in special cases.
[0023] The manner of operation in the wetting or spraying of the
fins of the heat exchanger results in substantial energy and water
savings in comparison with customary methods such as with open
cooling towers. However, the restriction in the choice of material
of the wetted or sprayed heat exchanger in conjunction with the fin
where corrosion may not occur in connection with an electrolyte is
disadvantageous.
[0024] Hybrid heat transfer is thus understood as the substantial
improvement of the heat transfer of fin heat exchangers with pipes
by direct wetting or spraying of water. It is above all necessary
in this respect to regulate the air speed in the fin packet so that
no taking along of water occurs at the fin surface. This is
advantageously achieved by a speed regulation of the fans or by
other suitable measures.
[0025] It is a disadvantage in this respect that the sprayed or
wetting water acts as an electrolyte together with dissolved ions,
which can result in numerous corrosion problems with the usually
used material pairings of copper pipe and aluminum fins of the heat
exchanger.
[0026] It is known in this respect e.g. to use so-called
cataphoretic dip coating as a suitable surface protection for heat
exchangers. Furthermore, both the material pairings such as copper
pipe and copper fin and aluminum pipe and aluminum fin as well as
stainless steel pipe and stainless steel fin are used to master the
problems of contact corrosion. It is also known to zinc coat the
heat exchangers completely. High demands are made on the quality of
the circulation water or spray water in this respect with regard to
the pH values, water hardness, chlorine content, conductivity, etc.
to prevent deposits from forming, on the one hand, on condensation
on the fin due to evaporation and from contents of chemically
reactive materials which are too high forming, on the other hand,
which can on their part result in corrosion together with the
deposits.
[0027] To achieve higher heat transfer capacities than are e.g.
known with small heat exchangers from automotive engineering or
domestic technology, attempts have previously been made to make use
of the previously described hybrid technology with larger heat
transfer systems.
[0028] Another possibility to reach larger heat transfer capacities
basically involves trying to achieve greater exchange capacities by
interconnection of a plurality of individual heat exchange
components, e.g. by the connection of Al-MCHX modules.
[0029] One problem with all previously known heat exchanger systems
is, however, that the heat transfer capacity of an existing heat
exchange system cannot be adapted at all or only with very large
difficulties, that is ultimately only with a great effort and
substantial costs. This applies both to an increase and to a
decrease of the heat transfer capacity of an existing system.
[0030] These known difficulties are due to different reasons.
[0031] The known heat transfer systems are as a rule closed units
whose heat transfer capacity can at best be regulated within
certain narrow limits in that, for example, the throughflow
quantity of a refrigerant is regulated by the heat exchanger or the
quantity of the cooling medium, e.g. of cooling air, is varied by
the regulation of the suction performance of a fan. It is also
possible to reduce the quantity of cooling air, for example, in
that the heat exchanger has adjustable air sealing flaps so that
the throughflow rate of cooling air supplied to the heat exchanger
is thereby adjustable.
[0032] However, the performance of a heat exchange system can only
be varied between zero and a maximum heat exchange rate by all
these known measures. An increase of the heat transfer capacity
beyond a system-induced maximum value is not possible thereby.
[0033] It is also not possible as a rule or is in particular not
possible or meaning for economic and/or technical reasons to make
the heat transfer capacity of an existing heat exchange system as
small as desired or to reduce it to zero. That is the known heat
transfer systems always have to be operated at a specific maximum
heat transfer capacity, which frequently makes the operation
unnecessarily inefficient, but cannot be avoided.
[0034] If therefore, for example, the heat transfer capacity of an
existing heat exchange system should be reduced efficiently, for
example because the size of an associated cold store was
substantially reduced, no other possibility has previously been
available than to replace the existing heat exchange system with
another with correspondingly lower performance.
[0035] If, conversely, the heat transfer capacity of an existing
heat exchange system should be significantly increased because, for
example, an associated cold store has to be made hugely larger, no
other economic alternative as a rule often also remains in this
case in practice than to replace the existing heat transfer system
by a system with a higher heat transfer capacity. The heat transfer
capacity of existing systems can therefore not be increased
efficiently in a simple manner, that is above all under economic
aspects. Purely from a construction aspect, it is not simply
possible, for example, to add an additional heat exchanger to a
known heat transfer system with a given heat transfer capacity.
Additional heat exchangers cannot simply be attached in or to the
existing housing constructions and be connected to the existing
cooling circuits from a purely geometric aspect.
[0036] Even where the this would be realizable in principle under
purely geometric aspects with difficulty, such an expansion is
often technically so complex and/or expensive that such a change is
not worthwhile.
[0037] A possibility of increasing the heat transfer capacity of an
existing system is naturally generally to install a second
additional system. However, new problems also occur in practice
here which often do not permit such a solution.
[0038] An additional heat exchange system can namely not be
integrated without problem into the existing control and regulation
electronics. First, corresponding control systems are simply
technically not designed to control a further heat exchange system
so that additional control electronics have to be installed. If
both heat exchange systems, however, for example, they have to be
operated simultaneously for the cooling of one and the same
enlarged cold store, the coordination of the two independent
control systems is at least very difficult. In many cases, above
all when, for example, frequent and/or large changes in the cooling
capacity to be supplied are required, a reliable coordination of
the control system is not possible.
[0039] In many cases, however, for example, the installation of an
additional heat transfer systems is not possible for space reasons
alone.
[0040] This can, for example, be due to the fact that it is not
possible on site under the given space relationships to install
additional control electronics and/or additional cooling circuits
with the required refrigeration machines and the further components
known per se. However, the additional installation of the known
bulky heat exchange modules which include the heat exchangers, for
example in the form of finned heat exchangers and/or in the form of
microchannel heat exchangers, is also frequently not possible for
space reasons alone or is not desirable or is simply too complex
from a technical and economic aspect.
[0041] This ultimately means that the required power density is not
reached in an expanded heat exchange system because the expansion
of an existing heat exchange system by additional heat exchange
modules cannot take place sufficiently compactly purely for
geometrical reasons.
[0042] Furthermore, the question of the deficient power density of
the known heat exchange systems is a problem in many areas which
has generally not yet been solved. Particularly where a large
quantity of heat has to be transferred in a very small space in as
short a time as possible, for example with large electronic systems
such as with very powerful data processing systems or other systems
known to the skilled person per se, the power densities of known
heat exchange systems are often not sufficient. The only solution
is then frequently installing the heat exchange modules with the
heat exchangers at a very distant location where there is
sufficient space for the heat exchange modules which are not
compact enough, with all the known technical and economic
disadvantages.
[0043] It is therefore the object of the invention to provide an
improved heat exchange system which overcomes the problems known
from the prior art and with which, in particular due to a compact
construction, high cooling performance can be achieved, on the one
hand, in a minimal space, that is higher power densities can be
achieved in the heat transfer. On the other hand, a heat exchange
system should simultaneously be provided whose heat transfer
capacity can be changed easily in a very flexible, technically
simple and economically efficient manner, that is can be both
increased and decreased in very wide limits.
[0044] The subjects of the invention satisfying these objects are
characterized by the features of independent claim 1.
[0045] The dependent claims relate to particularly advantageous
embodiments of the invention.
[0046] The invention thus relates to a modular heat exchange system
having a heat exchange module which includes at least one first
heat exchange module with a heat exchanger. In this respect, an
outer boundary of the heat exchange module is formed by an inflow
surface and an outflow surface such that, for the exchange of heat
between a transport fluid and a heat agent flowing through the heat
exchanger in the operating state, the transport fluid can be
supplied to the heat exchange module via the inflow surface, can be
brought into flow contact with the heat exchanger and can be led
away again from the heat exchange module via the outflow surface.
In accordance with the invention, a first boundary surface of the
first heat exchange module is inclined at a presettable angle of
inclination with respect to a second boundary surface of the first
heat exchange modules.
[0047] It is important for the invention that with a modular heat
exchange system of the present invention a first boundary surface
of a first heat exchange module is inclined at a presettable angle
of inclination with respect to a second boundary surface of the
first heat exchange module.
[0048] By a suitable choice of the angle of inclination, which is
particularly preferably not equal to 90.degree., the invention thus
provides a heat exchange system of modular design which can be
expanded substantially periodically or non-periodically in one, two
or three spatial dimensions depending on the embodiment by
stringing together preferably identically heat exchange modules,
but can also be made smaller in that one or more heat exchange
modules are simply removed from an existing system.
[0049] The suitable choice of the angle or inclination or the
specific choice of the mutually inclined surfaces in this respect
decisively determines whether a periodic expansion is possible in
one, two or three dimensions or determines the maximum number of
heat exchange modules which can be combined to form a modular heat
exchange system in accordance with the invention.
[0050] If e.g. the outer shape of a triangular prism with an angle
of inclination of 60.degree. is selected for the construction shape
of the heat exchange module, a maximum of six heat exchange modules
of this kind can be combined to form a very compact heat exchange
system of hexagonal structure which have a very high power density
with respect to the heat transfer.
[0051] If the heat exchange performance should be reduced due to
new demands in such a hexagonal heat exchange system made up of six
heat exchange modules, the required number of heat exchange modules
can simply be removed from the hexagonal heat exchange system.
[0052] If in another case, for example, the heat exchange modules
are therefore made in the form of a parallelepiped having an angle
of inclination of 45.degree., two respective such heat exchange
modules can be assembled in a particularly compact manner, e.g. via
the inclined surfaces, and can also, if required, be expanded as
desired by being strung next to one another.
[0053] The heat transfer capacity and/or the power density of the
heat transfer can thus be matched in a simple and efficient manner
by a modular heat transfer system of the present invention by the
regular repetition of preferably identical heat exchange modules or
by the removal of identical heat exchange modules.
[0054] In a particularly preferred embodiment, the first boundary
surface of the first heat exchange module is thus inclined at the
presettable angle of inclination with respect to the second
boundary surface of the first exchange module such that the modular
heat exchange system can be expanded by a second heat exchange
module, in particular in a compact construction shape, with the
second heat exchange module preferably being identical to the first
heat exchange module. In this respect, compact construction shape
means that two heat exchange modules can be combined with one
another in as space saving a manner as possible so that as little
free space as possible, preferably practically no free space at
all, remains between two combined heat exchange modules.
[0055] In a particularly simple, particularly compact and thus
cost-effective construction shape, the heat exchanger itself has a
supporting function in the formation of the heat exchange module.
This can, for example, be realized in that the heat exchanger
itself forms a housing wall of the heat exchanger module or in that
the housing of the heat exchanger module does not have a boundary
wall at all the boundary surfaces of the housing so that the heat
exchanger itself satisfies a connecting and stabilizing integral
static function as a housing component.
[0056] As mentioned, particularly important significance accrues to
those embodiments in accordance with the invention in which the
heat exchange system is formed from a plurality of heat exchange
modules since the heat transfer capacity can be reduced
particularly simply in them, for example, by removal of a heat
exchange module.
[0057] The angle of inclination between the first boundary surface
and the second boundary surface of the heat exchange module is
advantageously between 0.degree. and 180.degree., specifically
between 20.degree. and 70.degree., preferably between 40.degree.
and 50.degree., and the angle of inclination particularly
preferably amounts to 45.degree..and/or the angle of inclination is
between 90.degree. and 180.degree., in particular at
120.degree..
[0058] In a specific embodiment in accordance with the invention,
the angle of inclination between the first boundary surface and the
second boundary surface of the heat exchange module has a value of
360.degree./n for the formation of a heat exchange system in the
form of a heat exchange cluster, where n is a whole number and the
heat exchange cluster is preferably formed from a number of n
identical heat exchange modules, with the angle of inclination
between the first boundary surface and the second boundary surface
of the heat exchange module being 60.degree. for the formation of a
hexagonal heat exchange cluster, for example, with the hexagonal
heat exchange cluster preferably being formed from six identical
heat exchange modules for the achieving of a maximum heat exchange
performance and/or a maximum power density of the heat
exchange.
[0059] In a further simple embodiment, a boundary surface of the
heat exchange system can be dispensed with at its housing, with the
omitted housing wall being formed in the installed state of the
heat exchange system by a wall of an installation object, in
particular being formed by a wall of a housing.
[0060] For the further increase of the power density of the heat
transfer between the heat transfer agent and the transport fluid
and/or for the increase of a heat transfer rate between the heat
transfer agent and the transport medium, a cooling device can be
provided for the cooling of the heat exchanger, in particular a fan
for the generation of a gas flow, and/or the heat exchange system
can, as known per se and as initially described in detail, be made
as a hybrid system, and a sprinkling device can be formed for the
sprinkling of the heat exchanger with a cooling fluid, in
particular with cooling water. In this respect, a drop separator
can also particularly advantageously be provided for the separation
of the cooling fluid.
[0061] In this respect, the heat exchanger itself, as known per se
from the prior art, can be made by a plurality of microchannels as
a microchannel heat exchanger and/or the heat exchanger can also be
made as a fin heat exchanger with cooling fins. Specifically, the
heat exchange system can be made as a combination heat exchange
system of the fin heat exchanger and the microchannel heat
exchanger if specific demands prefer such a construction shape.
[0062] To improve the possibilities of regulating the heat transfer
capacity of a heat exchange system in accordance with the
invention, a sealing, in particular an air sealing, can be provided
for the regulation of a flow rate of the transport fluid which can
be controlled and/or regulated either manually or via a control
unit in dependence on a presettable operating parameter.
[0063] A compensation means known per se can very advantageously
also be provided for the compensation of thermomechanical
strains.
[0064] The components of the modular heat exchange system of the
present invention, that is, for example, the heat exchangers and/or
a supply line and/or a leading away line for the heat transfer
agent and/or every other component of a heat exchange system in
accordance with the invention, can be connected by a universal
connection element to every other component of the heat exchange
system so that, for example, a heat exchange module can be added or
removed particularly easily. Specifically, the inlet tanks and
outlet tanks for the heat transfer agent or also sheet metal parts
and other modules and components of the heat exchange system are
particularly preferably connected to a universal connection
element. In this respect, these universal connection elements are
particularly well suited both for the vertical installation and for
the horizontal installation of the heat exchange systems or of the
heat exchange modules.
[0065] In addition, a cleaning system can furthermore be provided,
specifically including a dust capturing grid and/or a scraper
and/or a washing device, in particular a cleaning opening and/or a
cleaning flap, so that the heat exchange system or its components
such as the heat exchange module or other components can be cleaned
simply and efficiently. In addition to other possible embodiments,
in this respect the heat exchanger can, for example, be provided at
the cleaning flap and/or the heat exchanger itself can be made as a
cleaning flap.
[0066] However, as a rule, but not necessarily, a control unit, in
particular a control unit having a data processing system for the
control of the cooling device and/or of the cleaning system and/or
of the air sealing and/or of an operating or state parameter of the
heat transfer agent and/or of another operating parameter of the
heat exchange system will be provided for the control and/or
regulation of the heat exchange system in the operating state, as
is known to the skilled person per se from the prior art with
existing heat exchange systems.
[0067] The heat exchange system or the heat exchange module and/or
the heat exchanger and/or a boundary surface of the heat exchange
module, specifically the total heat exchange system, is
particularly advantageously produced from a metal and/or a metal
alloy, in particular from a single alloy, and can in particular be
produced from stainless steel, specifically from aluminum or from
an aluminum alloy, with a sacrificial metal preferably being
provided as corrosion protection and/or with the heat exchange
system being partly provided with a protective layer, in particular
with a corrosion protective layer. Particularly the inlet tanks and
outlet tanks are preferably produced for high pressures, for
example for operation with CO.sub.2, from very strong materials
such as stainless steel.
[0068] A heat exchange system in accordance with the invention is
specifically a radiator, in particular a radiator for a vehicle,
specifically for a land vehicle, for an aircraft or for a water
vehicle, or a cooler, a capacitor or an evaporator for a mobile or
stationary heating plant, refrigerating plant or air-conditioning
plant, in particular a cooler apparatus for a machine, a data
processing system or for a building or for another apparatus which
can be operated with a heat exchange system.
[0069] The invention will be explained in more detail in the
following with reference to the drawing. There are shown in a
schematic representation:
[0070] FIG. 1 a first embodiment of a heat exchange system in
accordance with the invention;
[0071] FIG. 2 a heat exchanger in accordance with FIG. 1 with
microchannels;
[0072] FIG. 3 an element of a finned heat exchanger;
[0073] FIG. 4a an embodiment in accordance with FIG. 1 with air
sealing;
[0074] FIG. 5a a third embodiment in accordance with FIG. 1 with a
cleaning flap;
[0075] FIG. 5b the embodiment of FIG. 5a during a cleaning
process;
[0076] FIG. 6a another embodiment of a heat exchange system in
accordance with the invention with a universal connection
element;
[0077] FIG. 6b a universal connection element of FIG. 6a in
detail;
[0078] FIG. 7 a heat exchange system with two heat exchange
modules.
[0079] FIG. 8a a first known heat exchange system for operation
with vertical installation;
[0080] FIG. 8b a second known heat exchange system for operation in
horizontal installation;
[0081] FIG. 9 a heat exchange system in accordance with the
invention for operation in vertical installation;
[0082] FIG. 10 a heat exchange system in accordance with the
invention for operation in horizontal installation;
[0083] FIG. 11 a further heat exchange system made up of four heat
exchange modules;
[0084] FIG. 12 a first embodiment of a heat exchange cluster in
hexagonal form;
[0085] FIG. 13 a second embodiment in accordance with FIG. 12;
[0086] FIG. 14 another embodiment of a heat exchange cluster.
[0087] FIG. 1 shows in a schematic representation a first simple
embodiment of a heat exchange system in accordance with the
invention which is provided as a whole with the reference numeral 1
in the following.
[0088] The heat exchange system 1 in accordance with the invention
of FIG. 1 includes as a major element a heat exchange module 2, 21
having a heat exchanger 2 for the exchange of heat between a heat
agent 7, e.g. a cooling liquid 7 or an evaporating agent 7, and a
transport fluid 6, e.g. air 6. The heat exchanger 3 in the present
case is a microchannel heat exchanger 3 known per se with a
plurality of microchannels 10. The microchannels 10 of the heat
exchanger 3 are connected via a connection system, which is not
shown in FIG. 1 and which is generally known to the skilled person,
to a refrigeration machine, likewise not shown, for the exchange of
heat transfer agent 7.
[0089] The refrigeration machine is flow connected in a manner
known per se to the connection system, including an inlet channel
with an inlet segment of the heat exchanger 3 and an outlet channel
with an outlet segment of the heat exchanger 3, such that the heat
transfer agent 7 for the exchange of heat with the air 6 can be
supplied from the inlet channel via the inlet segment, through the
plurality of microchannels 10 of the heat exchanger 3 and finally
via the outlet segment to the outlet channel.
[0090] An outer boundary of the heat exchange module 2 is in this
respect formed by an inflow surface 4 and an outflow surface 5 such
that in the operating state for the exchange of heat between the
transport fluid 6, whose flow direction is shown symbolically by
the arrows 6, and the heat transfer agent 7 flowing through the
heat exchanger 3, the transport fluid 6 can be supplied to the heat
exchange module 2 via the inflow surface 4, can be brought into
flow contact with the heat exchanger 3 and can be led away again
from the heat exchange module 2 via the outflow surface 5.
[0091] So that the heat can be exchanged better between the air 6
and the heat transfer agent 7, a cooling device 9 is additionally
provided, in the present case a fan 9, with which a quantity of air
6 can be controlled which is conveyed through the heat exchange
module 2, 21 per time unit.
[0092] In this respect, a first boundary surface 81 of the heat
exchange module 2, 21 which is formed in the present case by the
heat exchanger 3 itself, is inclined with respect to a second
boundary surface 82, 83 of the first heat exchange module 2, 21 at
a presettable angle of inclination .alpha. which amounts to
approximately 35.degree. in the present specific example. It is
understood that in another embodiment the angle of inclination
.alpha. can also have a different value, e.g. a value greater or
smaller than 35.degree., e.g., but not only, 25.degree. or
45.degree.. In the simple embodiment in accordance with FIG. 1, in
this respect, the second boundary surface 82, 83 is formed by a
wall 800 of an installation object which in the present case is a
cold store not shown in any more detail.
[0093] A heat exchanger 3 in accordance with FIG. 1 with
microchannels 10 is shown schematically in section in FIG. 2.
Instead of small pipes such as are used in the classical finned
heat exchangers 3 in accordance with FIG. 3, as already mentioned,
extruded aluminum sections are e.g. used in minichannel heat
exchangers 3 which have very many small channels 10 with a diameter
of e.g. approximately 1 mm. The heat exchanger 6 of FIG. 2 can e.g.
be manufactured simply and in a variety of shapes from a plurality
of materials in a suitable extrusion process. In this respect, the
heat exchanger 3 in accordance with FIG. 2 can also be manufactured
in an embodiment variant not explicitly shown in FIG. 2, such as
e.g. by the assembly of suitably shaped sheet metal sections or by
other suitable processes.
[0094] In contrast to FIG. 2, FIG. 3 shows an element of a finned
heat exchanger 3 known per se with cooling fins 300 such as could
likewise be used instead of a microchannel heat exchanger 3 in an
embodiment of the present invention. The heat transfer agent 7
flows through the tubular element of the finned heat exchanger 3
which, in the operating state, mainly exchanges heat via the
cooling fins 300 with the air 6 flowing past. It is understood that
in practice the heat exchanger 3 is as a rule made from a plurality
of elements in accordance with FIG. 3. In a very special embodiment
of the present invention, which is not shown explicitly with
reference to a drawing for space reasons, a combination heat
exchanger 3 is used as the heat exchanger 3. This means that a heat
exchange system 1 of the present invention can simultaneously
include, in addition to a heat exchanger 3 with a plurality of
microchannels 10, a finned heat exchanger 3 with cooling fins 300
for very special applications.
[0095] To cope with any even larger heat transfer capacities, the
heat exchange system 1 can also be made as a so-called hybrid
system 1 whose functional principle is likewise known to the
skilled person per se and therefore does not have to be shown
explicitly with reference to a separate drawing. In this case, a
sprinkling device is preferably provided for the sprinkling of the
heat exchanger 3 with an external cooling fluid, in particular with
cooling water or cooling oil. Specifically, a drop separator can
additionally be provided e.g. in the form of a pan for the
separation and collection of the external cooling fluid in the
operating state so that the external cooling fluid can be recycled
in an external cooling system which serves for the cooling of the
external cooling fluid and can be supplied to the heat exchanger 3
again via the sprinkling system for the repeat cooling of the heat
exchanger.
[0096] A second simple embodiment in accordance with FIG. 1 is
shown schematically with an air sealing 11 in FIG. 4. The air
sealing 11 is preferably made in the form of a sun blind or of a
Venetian blind, including individual sun blind elements 111 or
Venetian blind elements 111, so that the degree of covering of the
heat exchanger 3 can be changed variably, preferably in
electronically controlled and/or regulated form, in that the air
sealing is removed in a known manner, wholly or partly for example,
from the surface of the heat exchanger 3 by gathering together the
individual sun blind elements 111 or Venetian blind elements 111 or
in that an angle between the individual Venetian blind elements 111
and the surface of the heat exchanger 3 is changed so that the
effective passage area for the air 6 can be varied. A regulation of
the heat exchange performance of the heat exchanger 3 is thereby
possible in a simple manner without changing the flow dynamics in
the cooling system.
[0097] FIGS. 5a and 5b show a third embodiment in accordance with
FIG. 1 with cleaning flap 121, with FIG. 5a showing the heat
exchange system 1 briefly before a cleaning process in which the
interior, in particular the surface, of the heat exchanger 3 should
be freed from dirt which unavoidably collects in the operation of
the heat exchange system. FIG. 5b shows the heat exchange system 1
during the cleaning process.
[0098] The cleaning flap 121 is designed as an access flap 121
which is made rotatable around the axis of rotation 122 in
accordance with the arrow P so that an access is provided by a
pivoting of the cleaning flap 121 around the axis of rotation 122,
which can be made as a universal connection system 13, for example,
said access enabling service and repair and cleaning work simply in
the interior without the heat exchange system 1 having to be
disassembled.
[0099] FIG. 5b shows a situation in which the heat exchanger 3 is
just being cleaned with a cleaning liquid 123, for example with
water 123. The cleaning flap 121 was pivoted, starting from the
situation of FIG. 5a, around the axis of rotation 122 such that it
acts, in accordance with FIG. 5b, as a collection pan 121 which
reliably collects the contaminated cleaning liquid 123 during the
cleaning process so that the contaminated cleaning liquid can be
led away and disposed off safely, and optionally automatically, so
that damage to the environment is avoidable, for example.
[0100] Another embodiment of a heat exchange system in accordance
with the invention is shown schematically in FIG. 6a in which the
cleaning flap 121 is fastened to a universal connection element 13
in accordance with FIG. 6b. The universal connection element 13 is
inter alia suitable for the simple and reliable connection of inlet
tanks and outlet tanks known per se and not shown explicitly in
FIGS. 6a and 6b which serve for the supply or leading away of the
heat transfer agent 7 to or from the heat exchanger 3
respectively.
[0101] The universal connection element 13 is preferably designed
such that it can be connected to the corresponding parts of the
heat exchange system 1 particularly simply via a screw connection,
for example, or by soldering.
[0102] It can serve for the connection of lines which conduct heat
transfer agent 7 or can even itself be suitable as a line for the
conveying of heat transfer agent 7. It can furthermore be suitable
for the connection of sheet metal parts such as the cleaning flap
12 or other parts. In a given modular heat exchange system 1, the
universal connection element 13 is preferably made in detail such
that it can provide as many different connections as possible
simultaneously in one and the same embodiment so that as few
differently made universal connection elements as possible have to
be used simultaneously in one and the same modular heat exchange
system 1.
[0103] In the ideal case, the universal connection element 13 is
made such that it can simultaneously take over all connection
functions between all parts of the modular heat exchange system so
that only one single type of universal connection element has to be
used in one and the same heat exchange system 1, which hugely
simplifies the structure, the expansion or the reduction of a
modular heat exchange system 1 in accordance with the invention and
thus guarantees very high flexibility of the system.
[0104] FIG. 7 shows a modular heat exchange system 1 in accordance
with the present invention which includes two identical heat
exchange modules 2, 21, 22. The two modules are of identical
construction shape, with the angle of inclination .alpha. having a
value of 45.degree.. The skilled person will immediately understand
that generally as many identical heat exchange modules 2, 21, 22 as
desired can be added in both directions of the double arrow DP.
This means that only one single type of heat exchange modules 2,
21, 22 has to be provided to change the heat exchange performance
of the modular heat exchange system 1 to provide a system 1 with
practically any desired presettable heat exchange performance or to
expand it or to reduce the heat exchange performance in an existing
system by a reduction of the number of the heat exchange modules 2,
21, 22. The individual heat exchange modules 2, 21, 22 are
particularly preferably integrated in the heat exchange system 1 by
use of the universal connection elements 13, as was already
discussed with reference to FIG. 6a and FIG. 6b.
[0105] In addition to the huge flexibility which a heat exchange
system 1 in accordance with the invention shows with respect to the
number and the possibilities of the arrangement of the heat
exchange modules 2, 21, 22, a heat exchange system 1 in accordance
with the invention is also very flexible with respect to the
direction of building up or installation of the heat exchange
system 1.
[0106] Two heat exchange systems 1' known from the prior art are
shown very schematically in FIG. 8a and FIG. 8b.
[0107] For the better distinction of the prior art from the present
invention, those features which relate to examples from the prior
art are provided with a dash, whereas the reference numerals for
features in accordance with the invention do not have a dash.
[0108] A major disadvantage of the known heat exchange systems 1'
in accordance with FIG. 8a and FIG. 8b respectively is namely that
they can only be used, with respect to the direction of gravity S,
either only in the vertical installation direction, as shown in
FIG. 8a, or only in the horizontal installation direction in
accordance with FIG. 8b. In this respect, vertical means that the
outflow direction of the air 6' from the heat exchange system 1'
takes place substantially perpendicular with respect to the
direction of gravity S, whereas a horizontal direction of
installation meant that the air 6' flowing out of the heat exchange
system flows out substantially parallel or anti-parallel to the
direction of gravity.
[0109] The heat exchange system 1' of FIG. 8a, which was designed
for a vertical installation, can thus not be replaced by the heat
exchange system of FIG. 8b which is only designed for horizontal
installation.
[0110] The modular heat exchange system 1 in accordance with the
invention is also more flexible here, as is impressively
demonstrated with reference to FIGS. 9 and 10.
[0111] A heat exchange system 1 including two heat exchange modules
2, 21, 22 in a vertical installation manner is shown in FIG. 9; a
heat exchange system 1 in a horizontal installation manner is shown
in FIG. 10, with respect to the direction of gravity S in both
cases. In this respect, the individual heat exchange modules 2, 21,
22 of the heat exchange systems in accordance with FIG. 9 and FIG.
10 are completely identical. This means only one single type of
heat exchange modules 2, 21, 22 have to be provided to manufacture
both horizontally and vertically installable heat exchange systems
1. It is specifically even possible that one and the same heat
exchange system 1 simultaneously includes vertically oriented and
horizontally oriented heat exchange modules 2, 21, 22.
[0112] A further heat exchange system 1 of four heat exchange
modules 2, 21, 22 having two fans 9 in each case is shown by way of
example in FIG. 11, whereby the heat exchange performance of the
individual heat exchange modules 2, 21, 22 is substantially
increased. The skilled person will understand without problem that
the embodiment in accordance with FIG. 11 can advantageously also
be used both in the vertical and in the horizontal direction of
installation.
[0113] A first embodiment of a heat exchange cluster 1 is
furthermore shown in hexagonal shape by way of example in FIG. 12.
The modular heat exchange system 1 in the form of the heat exchange
cluster 1 in accordance with FIG. 12 includes six identical heat
exchange modules 2, 21, 22 which all have an angle of inclination
of 60.degree.. By the choice of this special geometry, it is
possible to combine the six heat exchange modules 2, 21, 22 to form
a hexagonal cluster, with the outwardly directed end faces of each
heat exchange module 2, 21, 22 being made as heat exchangers 3 or
the heat exchangers 3 being integrated into these outwardly
directed surfaces. In the operating state, the transport fluid 6,
that is the air 6, for example, is then sucked in via outwardly
directed surfaces including the heat exchangers 3 by the fans 9
which are provided in the boundary surfaces of the heat exchange
modules 2, 21, 22 directed perpendicular to the outwardly directed
faces.
[0114] This special construction manner as a heat exchange cluster
1 can always be used particularly advantageously when very high
heat transfer capacity is required in a very small space.
[0115] A second embodiment in accordance with FIG. 12 is shown in
FIG. 13. The embodiment of FIG. 13 substantially differs from that
in FIG. 12 in that the positioning of the fans 9 and the
positioning of the heat exchangers 3 is just swapped over. This
means that the fans 9 in the example of FIG. 13 are arranged in the
outwardly directed faces, whereas the heat exchangers 3 are
arranged in the faces perpendicular thereto in which the angle of
inclination .alpha. is disposed or the heat exchangers 3 form these
surfaces.
[0116] Finally, another embodiment of a heat exchange cluster 1 in
accordance with FIG. 12 is shown in FIG. 14 in a view from the
direction R in accordance with FIG. 12. The embodiment in
accordance with FIG. 14 differs from that of FIG. 12 in this
respect in that not six identical heat exchange modules 2, 21, 22
with an angle of inclination .alpha. of 60.degree. in each case
were used, but rather only five identical heat exchange modules 2,
21, 22 with an angle of inclination .alpha. of 72.degree. in each
case were used. Depending on the demand, generally any desired heat
exchange clusters 1 with a number of n identical heat exchange
modules 2, 21, 22 can thus be constructed, with each heat exchange
module 2, 21, 22 then having an angle of inclination .alpha. of
360.degree./n.
[0117] It is understood that the embodiments described within the
framework of this application are only to be understood as
examples. This means that the invention is not solely restricted to
the specific embodiments described. All suitable combinations of
the presented embodiments are in particular likewise covered by the
invention.
* * * * *