U.S. patent application number 14/319047 was filed with the patent office on 2014-12-25 for kit for a heat exchanger, a heat exchanger core, and heat exchanger.
The applicant listed for this patent is Behr GmbH & Co. KG. Invention is credited to Wolfgang SEEWALD, Falk VIEHRIG.
Application Number | 20140374072 14/319047 |
Document ID | / |
Family ID | 47520099 |
Filed Date | 2014-12-25 |
United States Patent
Application |
20140374072 |
Kind Code |
A1 |
SEEWALD; Wolfgang ; et
al. |
December 25, 2014 |
KIT FOR A HEAT EXCHANGER, A HEAT EXCHANGER CORE, AND HEAT
EXCHANGER
Abstract
A kit for producing heat exchangers includes at least two types
of heat exchanger cores in order to produce more than two different
heat exchangers. The kit has a first type of heat exchanger core
with a plurality of pairs of plates in order to produce a plurality
of parallel flow paths between the plate pairs and a second type of
heat exchanger core with a plurality of groups of three plates in
order to produce a plurality of second parallel flow paths, one
flow path being produced between two of each three plates.
Inventors: |
SEEWALD; Wolfgang; (Tamm,
DE) ; VIEHRIG; Falk; (Sindelfingen, DE) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Behr GmbH & Co. KG |
Stuttgart |
|
DE |
|
|
Family ID: |
47520099 |
Appl. No.: |
14/319047 |
Filed: |
June 30, 2014 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
PCT/EP2012/076859 |
Dec 21, 2012 |
|
|
|
14319047 |
|
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|
Current U.S.
Class: |
165/150 ;
29/726 |
Current CPC
Class: |
F28D 1/0426 20130101;
F28D 1/0408 20130101; F28D 1/0435 20130101; Y10T 29/53113 20150115;
F28D 1/05391 20130101; F28D 1/0333 20130101 |
Class at
Publication: |
165/150 ;
29/726 |
International
Class: |
F28D 1/053 20060101
F28D001/053 |
Foreign Application Data
Date |
Code |
Application Number |
Dec 30, 2011 |
DE |
10 2011 090 182.5 |
Claims
1. A kit for producing heat exchangers with at least two types of
heat exchanger cores for producing more than two different heat
exchangers, the kit comprising: a first type of heat exchanger core
with a plurality of pairs of plates to create a plurality of
parallel flow paths between the pairs of plates; and a second type
of heat exchanger core with a plurality of groups of three plates
to create a plurality of two parallel flow paths, one of the flow
paths arranged between two of the three plates, wherein a first
heat exchanger with a heat exchanger core of the first type is
provided, wherein a second heat exchanger with two heat exchanger
cores of the first type is provided, wherein a third heat exchanger
with a heat exchanger core of the first type and with a heat
exchanger core of the second type is provided, wherein a fourth
heat exchanger with two heat exchanger cores of the second type is
provided, and wherein a fifth heat exchanger with a heat exchanger
core of the second type is provided.
2. The kit according to claim 1, wherein the heat exchanger cores
of the first and/or second type are provided with connecting
devices and/or interconnecting devices for introducing and/or
discharging and/or transferring fluid into or between or out of the
heat exchanger cores.
3. A heat exchanger core in plate design for use in a kit according
to claim 1, for forming a heat exchanger with a plurality of plate
pairs for forming first flow paths, wherein two plates each of a
plate pair form the first flow path between them and a region for
second flow paths is formed between adjacent plate groups.
4. A heat exchanger core in plate design for use in a kit according
to claim 1, for forming a heat exchanger with a plurality of plate
groups for forming third and fourth flow paths, whereby the third
flow path is formed between a first and a second plate of a plate
group and the fourth flow path is formed between a second plate and
a third plate of the plate group, and a region for the fifth flow
path is formed between adjacent plate groups.
5. The heat exchanger core according to claim 3, wherein at least
individual plates have openings and/or cups as connecting and
interconnecting regions and have channel-forming structures or
embossings for forming flow paths between connecting regions.
6. The heat exchanger core according to claim 3, wherein the first
plate and second plate of the plate pair at two opposite end
regions each have a connecting region as an inlet or outlet of the
first flow path and a channel-forming structure between the two
connecting regions to form the first flow path.
7. The heat exchanger core according to claim 3, wherein the first
plate and/or second plate of the plate pair at an end region have
two connecting regions as an inlet or outlet of the first flow path
and have a channel-forming structure between the two connecting
regions to form the first flow path.
8. The heat exchanger core according to claim 4, wherein the first
plate, the second and third plate of the plate group at two
opposite end regions have two connecting regions as an inlet or
outlet of the third flow path or of the fourth flow path, wherein
the first and second plate between an opposite connecting region
have a channel-forming structure between one of the two connecting
regions to form the third and fourth flow path, and wherein the
third plate is provided between the first and second plate as a
partition wall between the third and fourth flow path.
9. The heat exchanger with at least two heat exchanger cores
according to claim, wherein a distance of the plate pairs or the
plate groups of a heat exchanger core to form the second and/or
fifth flow paths is selected such that in the case of adjacent heat
exchanger cores of a heat exchanger, it is the same or different,
such as smaller or larger than in the adjacent heat exchanger
core.
10. The heat exchanger according to claim 3, wherein a depth of the
flow channels perpendicular to the plane, defined by the plate
pairs or plate groups, is selected individually for each flow
channel.
11. The heat exchanger according to claim 3, wherein plate pairs
are formed from the paired arrangement of plates and with a
partition wall between adjacent plates, which form pairs of flow
channels, characterized in that flow through the flow channels of a
plate pair is a counterflow.
Description
[0001] This nonprovisional application is a continuation of
International Application No. PCT/EP2012/076859, which was filed on
Dec. 21, 2012, and which claims priority to German Patent
Application No. 10 2011 090 182.5, which was filed in Germany on
Dec. 30, 2011, and which are both herein incorporated by
reference.
BACKGROUND OF THE INVENTION
[0002] 1. Field of the Invention
[0003] The invention relates to a kit for producing a heat
exchanger in a plate design, particularly for motor vehicles, with
a plurality of plate pairs and/or plate groups for forming flow
paths, a heat exchanger core for forming heat exchangers, and a
corresponding heat exchanger.
[0004] 2. Description of the Background Art
[0005] Heat exchangers for motor vehicles are known in the
conventional art. Thus, heat exchangers are already being used in
many configurations and for many specific purposes in vehicles, for
example, as evaporators, storage evaporators, oil coolers,
condensers, charge air cooler, or coolant coolers. All of these
heat exchangers have different configurations and types of
construction, so that a different design is also often used for
each type.
[0006] DE 102006028017, which corresponds to U.S. Pat. No.
8,495,894, which is incorporated herein by reference, and which
discloses an evaporator with a cold store, a so-called storage
evaporator, in which an evaporator part is formed with double-row
flat tubes, whereby a storage part, which is formed as a single
row, is provided adjacent to said evaporator part of the heat
exchanger and through an arrangement of double tubes, on the one
hand, a refrigerant can flow through an inner flat tube and, on the
other, a cold store medium can be disposed in a space between the
inner flat tube and the outer flat tube or can flow through this
region.
[0007] In the conventional art, the production of a storage
evaporator is a highly complex process, because a plurality of
tubes and a plurality of parts must be fabricated and connected
together. The evaporator part is typically a variation of a
standard refrigerant evaporator, so that this structural element as
well cannot be used as a standard version, but requires
modification at least in regard to some structural elements. The
storage evaporator therefore represents a special solution that
cannot fall back on mass-produced parts.
[0008] EP 1817534 B1, which corresponds to U.S. Pat. No. 8,122,943,
discloses a storage evaporator, whereby in a first exemplary
embodiment flat tubes are again inserted into one another that can
be connected by means of connecting members to different
refrigerant or cold storage material-media circuits. The production
of such a storage evaporator again has a high parts complexity,
which results in considerable additional costs.
[0009] The embodiment of a storage evaporator in a plate design
according to the second exemplary embodiment of EP 1817534 B1 also
shows that a unique solution was again developed, which is of
limited suitability for other applications.
[0010] The heat exchangers in the conventional art are therefore
adapted very particularly to the requirements of the specific
medium in the circuit, so that wide use for different applications
is more likely to be ruled out.
SUMMARY OF THE INVENTION
[0011] It is therefor an object of the invention to provide a kit
for producing a heat exchanger in a plate design, particularly for
motor vehicles, with a plurality of plate pairs and/or plate groups
for forming flow paths, which facilitates the production of
different heat exchangers for different applications as well.
Moreover, it is also as object of the invention to provide heat
exchanger cores, which are used to form heat exchangers, and it is
the object of the invention to provide such a heat exchanger.
[0012] For the kit, this is achieved in an embodiment, whereby a
kit is provided for producing heat exchangers with at least two
types of heat exchanger cores for producing more than two different
heat exchangers, whereby the kit advantageously comprises a first
type of heat exchanger core with a plurality of pairs of plates to
create a plurality of parallel flow paths between the pairs of
plates and, further, comprises a second type of heat exchanger core
with a plurality of groups of three plates to create a plurality of
two parallel flow paths, whereby in each case a flow path is formed
between two of the three plates, whereby a first heat exchanger
with a heat exchanger core of the first type can be produced,
whereby a second heat exchanger with two heat exchanger cores of
the first type can be produced, whereby a third heat exchanger with
a heat exchanger core of the first type and with a heat exchanger
core of the second type can be produced, whereby a fourth heat
exchanger with two heat exchanger cores of the second type can be
produced, and a fifth heat exchanger with a heat exchanger core of
the second type can be produced. It is advantageous according to
the invention that the heat exchanger cores are designed in such a
way that they can be used alone, can be combined and used with
another core of the same type, and also can be combined and used
with a heat exchanger core of the other type.
[0013] As a result, when a heat exchanger core of the first type is
used as a simple, narrow evaporator, it can thus be used as
space-saving. This can occur advantageously in small vehicles with
low required cooling capacities.
[0014] In the case of higher required cooling capacities, if two
heat exchanger cores of the first type are used, these can be
arranged in a series or parallel connection to one another and used
so that an increased cooling capacity with a double space
requirement can be realized.
[0015] When the heat exchanger is used as a storage evaporator, a
heat exchanger core of the first type with a heat exchanger core of
the second type can be used, whereby in this case the refrigerant
can flow parallel or serially through flow paths of the first core
and of the second core, whereby the cold store medium can flow
through further flow paths of the second heat exchanger core.
[0016] Two heat exchangers of the second type can also be connected
together, so that, for example, an increased cooling capacity can
be realized with a simultaneous cold store effect.
[0017] Furthermore, the second type of heat exchanger core alone
can be used, for example, as a two-row evaporator or as a one-row
evaporator with a cold store. As a result, a storage evaporator
with a lower cooling capacity is realized, for example.
[0018] The heat exchanger cores of the first and/or second type can
be provided with connecting devices and/or interconnecting devices
for introducing and/or discharging and/or transferring fluid into
or between or out of the heat exchanger cores or between flow
channels of the heat exchanger cores.
[0019] With respect to the heat exchanger core, in an embodiment, a
heat exchanger core is provided in a plate design, particularly for
use in a kit, for forming a heat exchanger, with a plurality of
plate pairs for forming first flow paths, whereby in each case two
plates of a plate pair form the first flow path between them and a
region for second flow paths each is formed between adjacent plate
groups.
[0020] With respect to the heat exchanger core, in an embodiment, a
heat exchanger core is provided in a plate design, particularly for
use in a kit, for forming a heat exchanger, with a plurality of
plate pairs for forming third and fourth flow paths, whereby the
third flow path is formed between a first and a second plate of a
plate group and the fourth flow path is formed between a second
plate and a third plate of the plate group, and in each case a
region for the fifth flow path is formed between adjacent plate
groups.
[0021] At least individual plates can have openings and/or wells as
connecting and interconnecting regions and have channel-forming
structures, such as embossings, for forming flow paths between
connecting regions.
[0022] The first plate and second plate of the plate pair at two
opposite end regions in each case can have a connecting region as
an inlet or outlet of the first flow path and a channel-forming
structure between the two connecting regions to form the first flow
path.
[0023] The first plate and/or second plate of the plate pair at an
end region can have two connecting regions as an inlet or outlet of
the first flow path and a channel-forming structure between the two
connecting regions to form the first flow path.
[0024] The first plate, the second and third plate of the plate
group at two opposite end regions in each case can have two
connecting regions as an inlet or outlet of the third flow path or
of the fourth flow path, whereby the first and second plate in each
case between an opposite connecting region have a channel-forming
structure between one of the two connecting regions to form the
third and fourth flow path, whereby the third plate is provided
between the first and second plate as a partition wall between the
third and fourth flow path.
[0025] In an embodiment, heat exchangers with at least two heat
exchanger cores can have the distance of the plate pairs or the
plate groups of a heat exchanger core to form the second and/or
fifth flow paths selected in such a way that in the case of
adjacent heat exchanger cores of a heat exchanger, it is the same
or different, such as smaller or larger than in the adjacent heat
exchanger core.
[0026] The depth of the flow channels perpendicular to the plane,
defined by the plate pairs or plate groups, can be selected
individually for each flow channel.
[0027] Further, plate pairs can be formed from a paired arrangement
of plates and with a partition wall between adjacent plates, which
form pairs of flow channels, characterized in that flow through the
flow channels of a plate pair is a counterflow.
[0028] Further scope of applicability of the present invention will
become apparent from the detailed description given hereinafter.
However, it should be understood that the detailed description and
specific examples, while indicating preferred embodiments of the
invention, are given by way of illustration only, since various
changes and modifications within the spirit and scope of the
invention will become apparent to those skilled in the art from
this detailed description.
BRIEF DESCRIPTION OF THE DRAWINGS
[0029] The present invention will become more fully understood from
the detailed description given hereinbelow and the accompanying
drawings which are given by way of illustration only, and thus, are
not limitive of the present invention, and wherein:
[0030] FIG. 1 illustrates an arrangement of two heat exchanger
cores, a heat exchanger of a first type, and a heat exchanger of a
second type;
[0031] FIG. 2 illustrates an assembled arrangement of two heat
exchanger cores;
[0032] FIG. 3 illustrates an arrangement of two heat exchanger
cores of a first type;
[0033] FIG. 4 illustrates an arrangement of two heat exchanger
cores of a second type;
[0034] FIG. 5 illustrates a heat exchanger core of a first
type;
[0035] FIG. 6 illustrates a heat exchanger core of a second
type;
[0036] FIG. 7 illustrates two plates of a plate pair;
[0037] FIG. 8 illustrates three plates of a plate group;
[0038] FIG. 9 illustrates a number of plate pairs;
[0039] FIG. 10 illustrates a number of plates and a detail of a
plate;
[0040] FIG. 11a illustrates a plate in detail;
[0041] FIG. 11b illustrates a plate in a detail;
[0042] FIG. 11c illustrates a pair of plates of a plate group in a
detail;
[0043] FIG. 11d illustrates a pair of plates of a plate group in a
detail;
[0044] FIG. 12 illustrates an arrangement of plate pairs and plate
groups in a view;
[0045] FIG. 13 illustrates an arrangement of plate pairs with plate
groups in a view from the opposite side;
[0046] FIG. 14 illustrates an arrangement of plate pairs and plate
groups in a sectional cut through the plate pairs and the plate
groups;
[0047] FIG. 15 illustrates a plate with an overflow channel between
adjacent passages;
[0048] FIG. 16 illustrates the plate of FIG. 15 from the back;
[0049] FIG. 17 illustrates a view of a heat exchanger;
[0050] FIG. 18 illustrates the view of plate pairs;
[0051] FIG. 19 illustrates a view of plates;
[0052] FIG. 20 illustrates a section of plates;
[0053] FIG. 21 illustrates a section of plates;
[0054] FIG. 22 illustrates a section of plate pairs;
[0055] FIG. 23 illustrates a sectional cut through the plate pairs
according to FIG. 22;
[0056] FIG. 24 illustrates a sectional cut through the plate pairs
according to FIG. 22;
[0057] FIG. 25 illustrates a section of plate pairs;
[0058] FIG. 26 illustrates a sectional cut through the plate pairs
according to FIG. 25;
[0059] FIG. 27 illustrates a sectional cut through the plate pairs
according to FIG. 25;
[0060] FIG. 28 illustrates a schematic view of a heat exchanger;
and
[0061] FIG. 29 illustrates a schematic view of a plate pair.
DETAILED DESCRIPTION
[0062] FIG. 1 shows the arrangement of two heat exchanger cores 1,
2, which can be connected together to form a heat exchanger. In
this case, heat exchanger core 1 has a plurality of plate pairs 3,
which are arranged adjacent to one another, whereby corrugated fins
4 are arranged in free spaces between the particular adjacent plate
pairs for better heat transfer during the flow of air between the
particular adjacent plate pairs 3. As a feed and discharge, plates
3 at their opposite ends have connections or openings, formed as
such as cups 5, 6, which are also used to connect plate pairs 3 to
one another.
[0063] Heat exchanger core 2 is formed with a plurality of plate
groups 7, whereby again adjacent plate groups 7 leave free spaces 8
for the flow of air, whereby a mount for corrugated fins can be
provided for improved heat exchange for the flow of air.
[0064] FIG. 1 thus shows an arrangement of two heat exchanger cores
1, 2, whereby first heat exchanger core 1 is a heat exchanger core
of a first type, formed with a plurality of pairs of plates to
create a plurality of parallel flow paths between the pairs of
plates. Within the plate pairs, a flow path is created for a fluid
to flow through the plate, whereby entry and exit of the fluid into
the plate or out of the plate is permitted through a connecting
opening formed by a cup in the plate.
[0065] Second heat exchanger core 2 is a heat exchanger core of the
second type, which is formed with a plurality of groups of three
plates to create a plurality of two parallel flow paths, whereby in
each case a flow path is formed between two of the three plates. To
this end, the plate groups at their two opposite ends each have two
connecting openings for an inlet and outlet for a first and/or a
second fluid, so that either two different fluids can flow through
this heat exchanger core 2 in the particular different flow
channels, or also in a different application a fluid can flow in
different flow paths in two flows through the heat exchanger core,
whereby at one of the two heat exchanger core ends a redirection of
the fluid from the one flow path to the other flow path is then
provided. Said redirection is not shown in FIG. 1, however. In this
regard, reference is made to FIGS. 15 and 16, which show a plate
200, where an overflow channel is provided as redirection between
cups 201. Inlets and outlets in second heat exchanger core 2 are
evident in the circular or substantially circular openings 10, 11,
which are arranged at the top or bottom end region of the
particular plate group. The plurality of adjacent plate groups form
an inlet and outlet distribution channel via cup-shaped openings
10, 11 as connecting regions, so that a fluid flowing into the heat
exchanger core through opening 10, 11 and the corresponding cup can
be distributed over the length of the heat exchanger core before it
can flow through the flow channels along the heat exchanger plate
group, before it is again collected at the opposite end in the area
of the cup connection, before the fluid can be conveyed out of the
heat exchanger. This applies both to the flow channel between the
first and the second plate and between the second and third plate.
It is evident that opening 10 is adjacent to opening 11 and has a
smaller cross section, so that different flow rates for the
different media can be realized throughout. However, in a further
exemplary embodiment it can also be expedient if openings 10, 11 of
the flow paths are of the same size.
[0066] FIG. 2 shows the arrangement of the two heat exchanger cores
1, 2 in an arrangement in which the heat exchanger cores are
connected to one another, whereby a heat exchanger is produced that
has a first core with a plurality of parallel flow paths, and has a
second core with a plurality of two adjacent flow paths.
[0067] Such a heat exchanger according to FIG. 2 can be used, for
example, as a storage evaporator, whereby a first flow path 12
between opening 5 and opening 6 is used as a refrigerant flow path
and then a redirection occurs to opening 11 as an inlet, so that
the refrigerant can flow through the flow path between the two
openings 11, 11a as connections and then can leave the evaporator.
Flow path 13 can be used between the openings as connections 10,
10a as the storage medium flow path, so that during normal
operation of the evaporator the storage medium in this flow path is
cooled and in case that the refrigerant circuit of the climate
control system is in a start/stop situation, for example, the
flowing air, indicated by arrow 14, is cooled further by the heat
exchange between the storage medium in flow path 13, so that also
during a temporary standstill phase of the refrigerant circuit of
the climate control system a certain cooling capacity can still be
provided during the start/stop operation.
[0068] It is advantageous, if a heat exchanger core of FIG. 1, as
labeled with reference character 1, can also be used as a single
heat exchanger, see FIG. 5, whereby such a heat exchanger 20 can be
used, for example, as a plate evaporator in a climate control
system with little available installation space. Said heat
exchanger 20 as an evaporator would in fact provide only a reduced
cooling capacity, but in small vehicles such as, for example, in
small electric vehicles, this might be completely sufficient. Heat
exchanger 20 has a core 25 of a plurality of plate pairs 26, which
are arranged spaced apart from one another, so that air can flow
through interspaces 24 and can be cooled thereby. The airflow
direction is indicated by arrow 27. Plate pairs 26 have connections
formed by cups, which are used to form the header space and are
used for the mutual attachment to adjacent plate pairs. A fluid can
flow into one connecting region, see arrow 21, and the fluid can
flow out again from an opposite connecting region, see arrow 22.
Flow path 23, formed by the plate pair and through which the fluid
flows lies between the two connecting regions.
[0069] Furthermore, two such heat exchanger cores according to
reference character 1 of FIG. 1 can be used in a parallel
connection or in a series connection, so that, for example, a
two-row evaporator unit can be formed by two heat exchanger cores
of the first type. This is shown in FIG. 3. FIG. 3 shows a heat
exchanger 30 made up of two heat exchanger cores 31, 32 of the
first type. Each of the two heat exchanger cores 31, 32 have a
plurality of plate pairs 33, 34, each of which is arranged spaced
apart from one another in a row in the particular core, so that,
for example, air can flow through interspaces 35, 36 between plate
pairs 33, 34 and can be cooled thereby. The airflow direction is
indicated by arrow 37. Plate pairs 33 have cup-shaped connections
38, 39, which are also used to form header spaces 40, 41 and are
used for the mutual attachment to adjacent plate pairs. Plate pairs
34 have cup-shaped connections 42, 43, which are also used to form
header spaces 44, 45 and are used for the mutual attachment to
adjacent plate pairs. For example, a fluid can flow into first core
31 in a connecting region 38. The fluid flows through flow channel
46 and can leave first core 31 at 39. It is redirected in order to
enter the second core at 43. Next, the fluid flows through second
flow channel 47 and out of an opposite connecting region 42 again
flows out of second core 32. The redirection is not shown; it can
occur through a tube or the like.
[0070] Alternatively, only one heat exchanger core according to
reference character 2 of FIG. 1 can be used (see FIG. 6), whereby
in this case a double flow is made possible, because each plate
assembly group already forms two flow paths, through which flow can
occur in different flow directions, so that this represents an
alternative to an evaporator, for example, which can be used when
only limited installation space is available. FIG. 6 shows a heat
exchanger 50 having only one heat exchanger core 51 of the second
type. Heat exchanger core 51 has a plurality of plate groups 52
which are arranged spaced apart from one another in a row, so that,
for example, air can flow through interspaces 53 between plate
groups 52 and can be cooled thereby. The airflow direction is
indicated by arrow 54. Plate pairs 52 form two parallel flow
channels 55, 56, each of which is formed by two of the three plates
of plate group 52.
[0071] The connections of the two flow channels or flow paths 55,
56 are formed by connections 57, 58, 59, 60, which are formed as
cups, which are also used to form the particular header spaces 61,
62, 63, 64 and are used for the mutual attachment to adjacent plate
pairs or plate group. In a connecting region 57 a fluid can flow
into first flow channel 55, for example. The fluid then flows
through flow channel 55 and as an outlet at cup 58 can leave first
flow channel 55. The fluid is then redirected in order to enter
second flow channel 56 at cup 59. Next, the fluid flows through
second flow channel 56 from cup 59 to cup 60 and there, at the
outlet located opposite to the inlet, again flows out of the second
flow channel. The redirection is not shown; it can occur through a
tube or the like.
[0072] Furthermore, it would be possible to combine two heat
exchanger cores according to reference character 2 of FIG. 1, i.e.,
two heat exchanger cores of the second type, to form a heat
exchanger, which provides four flow paths, therefore two flow paths
per heat exchanger core, in order to also enable four flows within
the provided installation space, for example. FIG. 4 shows such a
heat exchanger 70, which have only one first heat exchanger core 71
of the second type and one second heat exchanger core 72 of the
second type. In order to avoid repetitions, the mode of action of
the two heat exchanger cores 71, 72 will be explained according to
the heat exchanger core of FIG. 6. In this case, for example, a
fluid flows from a first core 71 and then is redirected to a second
core 72, and then flows through this second core 72, before the
fluid again leaves said core 72.
[0073] FIG. 7 shows two identically formed plates 80 and 81 of a
plate pair 82 and are arranged laterally reversed to one another.
The two plates each have a cup 83 and an opposite cup 84, which are
formed at opposite end regions of the plate. The cups point from
the base surface 85 of the plate in a direction perpendicular to
it, so that they protrude from base surface 85 of the plate.
Furthermore, the plate has a circumferential edge 86, which
projects in the direction perpendicular to the plane of plate 85,
whereby edge 86 projects in the opposite direction than cup 87 or
88 of openings 83, 84. If two plates are now connected to one
another, they rest against one another at circumferential edges 86
and can there be sealingly soldered together. This has the effect
that between the two plates a flow channel 89 arises that is used
for flow through the plate and is in fluid communication with
openings 83, 84.
[0074] FIG. 8 shows a plate group with plates 90, 91, and 92. In
this case, plate 90 has a base plane 93 and a correspondingly
projecting circumferential edge 94, whereby openings 95 and 96
formed by circumferential cups, are provided at the two opposite
ends, whereby the cups in regard to base plane 93 are embossed
perpendicular thereto and project in a different direction than
circumferential edge 94.
[0075] As is evident, flow channel 97 is embossed between openings
95 and is in fluid communication with them, whereby the flow
channel is separated from opening 96 and is not in communication
with it.
[0076] Plate 91 is formed planar and at the two opposite ends each
has openings 98, 99, which are formed without cups, whereby plate
91 is also formed planar and has no embossed structures. If plate
90 is now placed on plate 91, the two plates touch in the area of
circumferential edge 94 and can be connected together fluid-tight
so that, on the one hand, openings 98 are aligned with openings 95
and fluid channel 97 is defined between plate 90 and plate 91,
whereby openings 96 are aligned with openings 99, but are not in
communication with fluid channel 97.
[0077] Plate 92 also has openings 100, 101 at its opposite ends,
whereby in base area 102 of the plate a fluid channel 103 is formed
which communicates with openings 101, whereby a circumferential
edge 104 is formed projecting in a direction perpendicular to the
plane of base surface 102, whereby openings 100 are embossed in the
circumferential edge and thus are not in fluid communication with
flow channel 103. Openings 100 and 101 are designed with cups
projecting perpendicular to the direction of base plane 102,
whereby these project toward the back in FIG. 8 and thus project
opposite to circumferential edge 104.
[0078] If plate 92 is connected to plate 91, a fluid-tight
connection occurs in edge region 104 between the two plates,
whereby openings 99 and 101 are each aligned and create a fluid
communication to fluid channel 103, and openings 98 and 100 align
with one another but these openings do not have any fluid
communication with fluid channel 103. If plates 90, 91, and 92 are
now connected to one another, two fluid channels 97 and 103 arise,
which are separated from one another by the interposition of plate
91, and which are in communication with openings for the
introduction and discharge of a fluid. Thus, openings 95, 98, and
100 connect fluid channel 97 and openings 96, 99, and 101 connect
fluid channel 103.
[0079] FIG. 9 shows an arrangement of a plurality of plate pairs
according to FIG. 7, whereby plate pairs 110 are soldered together
and then connected to one another adjacently, so that they touch in
the region of projecting cups 111 and thereby define a distance
between the plate pairs that is greater than the extent of the
plate perpendicular to the base plane of the plate, so that a
region 112 remains open between the two neighboring plates for the
flow, for example, of air.
[0080] FIG. 10 shows a similar example of the arrangement of plate
groups 113 according to FIG. 8, whereby these plate groups are also
again connected together and adjacent plate groups come into
contact with one another via projecting cups 114, 115. A free space
116 is again opened between the plate groups for the flow, for
example, of air.
[0081] FIG. 11a shows a detail of a plate 82 according to FIG. 7,
as does FIG. 11b, whereby plate 82 has a planar base region 85
compared with which circumferential edge 86 projects, whereby
simultaneously opening 83 has a cup 87, which projects in a
different direction compared with base surface 85. This can also be
readily seen in FIG. 11b, so that cup 87 in FIG. 11b projects
forward compared with base surface 85, whereby circumferential edge
86 in FIG. 11b projects backwards.
[0082] A similar situation can be seen in FIGS. 11c and 11d for
plates 90 and 92, whereby plate 91 cannot be seen in this view of
FIGS. 11c and 11d. Plates 92 and 90 each have at their opposite
ends two openings 95 and 100 or 101 and 96, whereby these openings
are surrounded by cups, which project compared with base region 97
or 102 of the plates. As can be seen, flow channel 103 or flow
channel 97 is in fluid communication with another opening, so that
flow channel 97 is connected to opening 95, whereas flow channel
103 is connected to opening 101. If these plates are now placed one
on top of the other according to FIG. 8, small openings 95, 100 can
be connected to one another, while large openings 96 and 101 can be
connected to one another. Fluid channels 97 or 103 are designed as
to allow flow in conjunction with the particular openings, whereby
the two flow channels 97 and 103 are separated from one another by
the interposition of plate 91 (not shown).
[0083] FIG. 12 shows the arrangement of plate pairs and plate
groups in an adjacent arrangement, whereby the plate pairs of
plates 82 are arranged in the air flow direction ahead of the
arrangement of the plate groups of plates 90, 91, 92.
[0084] It can be seen that flow channel 85 is exposed to the air
flow first before flow occurs around flow channel 97 or flow
channel 103 (not shown). FIG. 13 shows this from the other side, so
that it can be seen that air first flows around flow channel 85
before it flows around flow channel 103. FIG. 14 shows this again
in a sectional cut, whereby it is evident that flow channel 85 is
formed by two plates 82, whereby flow channels 97 and 103 are
formed by plates 90, 91, and 92, whereby the two flow channels 90
and 103 in a direction perpendicular to the air direction together
only occupy the region occupied by air channel 85 of the two plates
82.
[0085] FIG. 17 shows a heat exchanger 300 with a heat exchanger
core, whereby heat exchanger core 301 is formed by a plurality of
plate pairs, arranged in parallel and having two plates, which by
the interposition of a partition wall form two flow paths between a
plate and the partition wall.
[0086] Heat exchanger 300 has a plurality of plate pairs 302,
arranged adjacent to one another, whereby corrugated fins 303 are
preferably arranged between the plate pairs. Each plate pair (also
see FIG. 18) has two inlet openings 304, 305, 306, 307, designed as
cups, at a first end region and at a second end region. In this
case, a cup of an end of region 304 or 305 forms an inlet-side cup,
whereby the outlet-side cup associated with flow path 308 is
arranged in the other end region. Accordingly, on each side in each
end region, an inlet-side and an outlet-side cup is provided as a
heat exchanger inlet or outlet.
[0087] FIG. 18 to this end shows three plate pairs, shown spaced
apart and having two plates and a wall inserted between them,
whereby these plate pairs are arranged to form a plate packet
310.
[0088] FIG. 19 shows the arrangement of a plate pair, having plates
311 and 312, whereby plate 311 forms a flow channel 313 and plate
312 a flow channel 314. These flow channels are formed by
embossings between two cups, whereby only two of the four shown
cups are connected to the flow channel. Thus, cup 315 and cup 316
are connected to flow channel 313, whereby cups 317 and 318 are not
connected to flow channel 313. In the case of plate 312, cup 319
and cup 320 are connected to flow channel 314, whereby cup 321 and
cup 322 are not connected to the flow channel. If the two plates
311 and 312 with the interposition of wall 323 are soldered
together, a fluid communication occurs between cups 315 and 321 and
316 and 322 and 318 and 319 and 317 with 320, so that cups 315, 321
are an inlet cup for flow channel 313 and cups 317 and 320 are an
outlet cup. The same applies to the arrangement of flow channel
314.
[0089] FIGS. 20 and 21 show the arrangements of cups 319, 321 of
FIG. 19 in an enlarged illustration, whereby cups 319 and 321 in
FIG. 20 are formed separated from one another and cup 319 is in
fluid communication with flow channel 314, whereas cup 321 is
separated from flow channel 314. FIG. 21 also shows two cups 330
and 331, whereby between the two cups 330 a crossover 332 is
provided, allowing a fluid overflow from cup 330 to cup 331.
[0090] FIG. 22 shows a plate packet with three plate pairs in a
perspective illustration with only the uppermost region of plate
packet 340 being shown. FIG. 23 shows a sectional cut along line 1
of FIG. 22 and FIG. 24 shows a sectional cut along line 2 of FIG.
22. It is evident that a plate pair 350, 351 each is provided with
an intermediate layer 352, whereby a flow channel 353 is arranged
between plates 350 and 351 on one side of partition wall 352, while
a second flow channel 354 is arranged on the other side of the
partition wall. This pattern repeats for each plate pair of the
three shown plate pairs, so that in each case two flow channels
354, 353 are arranged between the plate pairs on both sides of
partition wall 352.
[0091] FIG. 24 shows flow channels 353 and 354 likewise arranged on
one side of partition wall 352. FIG. 25 shows plate packet 340,
whereby FIG. 26 shows a sectional cut along line 3 of FIG. 25, and
FIG. 27 a sectional cut along line 4 of FIG. 25.
[0092] In FIGS. 26 and 27 plates 350 and 351 are shown with the
interposition of partition wall 352, whereby flow channels 354 and
353 can be seen. In sectional cut 3 it can be observed that the
flow channels do not run over the entire width of the plate,
whereas the flow channels in FIG. 27 run substantially over the
entire plate. This is so because the channel course toward the cup
must be reduced from the substantially full width to about half the
width.
[0093] A heat exchanger, has a row of plate pairs, can be formed by
the design of the plate pairs, whereby each half forms both a first
flow channel connected to an inlet header or to an outlet header
and a second flow channel, which is likewise provided with an inlet
header and an outlet header. In this case, the cups, connected
together in series, constitute the particular inlet header or
outlet header. The particular plate pair has two opposite plates,
whereby a partition wall or a partition sheet separating the flow
channels of the particular plates from one another, is provided
between the two plates. If the flow to the flow channels is a
counterflow, the partition sheet is used to separate the opposite
fluid flows through the flow channels, whereby the cups of the
individual plate pairs, arranged in series to one another, form the
fluid inlet header or the fluid outlet header.
[0094] FIG. 28 shows the schematic arrangement of plate pairs 400,
401, having an inflow-side cup 402 and an outflow-side cup 403. The
fluid flow occurs from the inlet-side cup 402 through flow channel
401 to a passover 404, from where the fluid can flow into second
flow channel 400, in order to flow to cup 403. This is carried out
with the plate pairs arranged next to one another in rows, whereby
the two flow channels 400 and 401 can be operated in counterflow to
one another.
[0095] FIG. 29 shows this in an enlarged illustration. Plate pair
401, 400 is provided with fins 405 on both sides for the flow of
air.
[0096] The invention relates to a heat exchanger with an internally
integrated heat transfer with two flow channels operated in
counterflow in a tube.
[0097] The configuration of a heat exchanger in a plate design is
described below; alternatively embodiments such as, e.g., those
with a flat tube design are also possible.
[0098] The heat exchanger has a row of plate pairs, half of which
in each case have both a first flow channel connected to the inlet
header or cup and a second flow channel connected to the outlet
header or cup. The plate pair is again made up of two opposite
plates and a partition sheet located between them. The partition
sheet is used to separate the opposite fluid flows; the connected
cups of the plate pairs, arranged in series, on the one hand, form
the fluid inlet header for distributing the fluid to the individual
first flow channels and, on the other, the fluid outlet header for
collecting the fluid from the individual two flow channels.
[0099] The two plates 311, 312 differ only in the transition region
between the plate channel and cups; in fluid inlet plate 311 a flow
connection is embossed between flow channel 313 and the fluid inlet
cup, whereby in the case of fluid plate 312 a connection between
flow channel 314 and the fluid outlet cup exists.
[0100] These connection embossings can be carried out alternately
in the plate tool and thus both plates can be produced in one and
the same tool with an interchangeable set. This reduces the tool
costs and increases the number of identical parts.
[0101] The flow through the above-described heat exchanger is such
that a fluid such as, for example, a refrigerant or coolant, etc.,
flows in over the first header as the inlet header, e.g., on the
top block side into the first plate channel half 311, then is
conveyed via a connecting element between the two opposite headers,
designated as the inlet header and outlet header at the lower block
side, into the second plate channel half 312, flows through it, and
then again flows out of this second channel half via the second
header, then again designated as an outlet header on the top block
side.
[0102] The advantage of this type of flow is the homogenization of
the temperature profile, e.g., as an evaporator, by an equalization
of the different temperatures of the opposite fluid flows based on
the heat transfer between the two channel halves, on the one hand,
and by an equalization of the temperature of the air flowing around
the two channel halves, on the other.
[0103] The connecting elements between the two opposite headers on
the bottom block side can be a separate connecting part or can also
be in a side part with an integrated redirection channel, or the
like.
[0104] In the case of a two-block connection, the fluid is
simultaneously distributed via the inlet header to all first plate
channel halves 311, arranged in parallel, and is distributed
further after the redirection by means of the connecting element to
all second plate channel halves 312.
[0105] In a multiblock connection, the fluid is distributed
simultaneously only to a certain number of first plate channel
halves 311, arranged in parallel, after which the fluid passover
occurs from one header to the neighboring header directly in the
plates, e.g., over embossed connecting channels between the
adjacent header cups of a plate, before--after flowing through the
second plate channel halves 312--the fluid is conveyed further into
the next block, and there the same distribution process continues
as in the first block.
[0106] The flow channel exchanger, such as particularly the plate
evaporator, alternatively can also be of a single-tank design,
i.e., with only one tank on one side of the heat exchanger.
[0107] The interconnection of the individual modules can vary,
depending on the arrangement and/or embodiment.
[0108] A pressure drop is produced in the evaporator depending on
the mass flow or operating point.
[0109] Depending on the pressure drop, different absolute pressures
arise and thereby different evaporation pressures between the
evaporator inlet and outlet.
[0110] This may cause the evaporation temperature at the evaporator
inlet at great pressure drops to be much higher than the
temperature associated with the evaporation pressure at the outlet.
Depending on the arising pressure drop across the heat exchanger,
this leads to a temperature response of the evaporating
refrigerant. In addition, overheating of the refrigerant at the end
of the evaporation at the evaporator outlet is desirable in order
to produce a stable overheating signal at the injection valve
(e.g., 5K).
[0111] However, this creates local hot zones in the evaporator,
which can be homogenized by suitable measures, such as, e.g.,
multiple interconnections one after the other in the air
direction.
[0112] By integration of an inner heat transfer surface in the
evaporator over substantially the entire height, local hot zones
between the evaporator inlet and outlet can be minimized.
[0113] A stable overheating in the counterflowing refrigerant at
the outlet can be produced between the incoming refrigerant by the
heat transfer at the integrated inner heat transfer surface.
Because of the much greater heat transfer, this occurs in a much
smaller section of the evaporator than in conventional systems with
multiple connections.
[0114] The temperature of the flowing refrigerant through the
evaporator reaches a lower average temperature level much quicker
and the overheating zone in the evaporator can be reduced to a
minimum. This results in a high driving average temperature
gradient and an increase in performance associated therewith.
[0115] The invention being thus described, it will be obvious that
the same may be varied in many ways. Such variations are not to be
regarded as a departure from the spirit and scope of the invention,
and all such modifications as would be obvious to one skilled in
the art are to be included within the scope of the following
claims.
* * * * *