U.S. patent application number 14/179653 was filed with the patent office on 2014-08-14 for condenser with a stack of heat exchanger plates.
The applicant listed for this patent is Modine Manufacturing Company. Invention is credited to Rebecca Frey, Klaus Kalbacher.
Application Number | 20140224455 14/179653 |
Document ID | / |
Family ID | 51226063 |
Filed Date | 2014-08-14 |
United States Patent
Application |
20140224455 |
Kind Code |
A1 |
Kalbacher; Klaus ; et
al. |
August 14, 2014 |
CONDENSER WITH A STACK OF HEAT EXCHANGER PLATES
Abstract
A condenser has a stack of heat exchanger plates that includes
at least a first section for condensation of a refrigerant and a
second section for supercooling the refrigerant. A refrigerant flow
channel and another flow channel for a liquid coolant stream are
formed in each of the first and second sections between the heat
exchanger plates that are in heat-exchanging relation. The stack of
heat exchanger plates is perforated by inflow and outflow channels
for the coolant stream and for the refrigerant, which are connected
to the at least one flow channel or the other flow channel. The
coolant stream can be divided into a coolant main stream and at
least one coolant partial stream, a throttle-like device is
arranged in the inflow channel to divert the at least one coolant
partial stream, and the at least one coolant partial stream is
positioned to supercool the refrigerant.
Inventors: |
Kalbacher; Klaus;
(Rangendingen, DE) ; Frey; Rebecca; (Esslingen,
DE) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Modine Manufacturing Company |
Racine |
WI |
US |
|
|
Family ID: |
51226063 |
Appl. No.: |
14/179653 |
Filed: |
February 13, 2014 |
Current U.S.
Class: |
165/104.21 |
Current CPC
Class: |
F28F 9/0251 20130101;
F28D 9/005 20130101; F28F 3/086 20130101; F28F 9/028 20130101; F25B
39/04 20130101; F28D 9/0093 20130101; F28D 2021/007 20130101 |
Class at
Publication: |
165/104.21 |
International
Class: |
F28F 3/08 20060101
F28F003/08; F25B 39/04 20060101 F25B039/04 |
Foreign Application Data
Date |
Code |
Application Number |
Feb 14, 2013 |
DE |
102013002545.1 |
Claims
1. A condenser comprising: at least one stack of heat exchanger
plates; at least a first section for condensation of a refrigerant;
and at least a second section for supercooling of the refrigerant,
wherein at least one flow channel for the refrigerant and at least
one flow channel for a liquid coolant stream are formed in each of
the first and second sections between the heat exchanger plates,
wherein the at least one flow channel for the refrigerant and the
least one flow channel for the liquid coolant are in
heat-exchanging relation, wherein the stack of heat exchanger
plates are perforated by inflow and outflow channels for the liquid
coolant stream and for the refrigerant, the inflow and the outflow
channels are connected to the at least one flow channel for the
refrigerant and the at least one flow channel for a liquid coolant
stream, wherein the liquid coolant stream is divided into a coolant
main stream and at least one coolant partial stream, and wherein a
throttle-like device is arranged in the inflow channel to divert
the at least one coolant partial stream, the at least one coolant
partial stream positioned to supercool the refrigerant.
2. The condenser according to claim 1, wherein the at least one
coolant partial stream is fed back to the inflow channel at least
mostly through at least one second flow channel for the liquid
coolant stream arranged in the second section.
3. The condenser according to claim 1, wherein the at least one
flow channel for the liquid coolant stream arranged in the second
section discharges directly in the outflow channel for the
coolant.
4. The condenser according to claim 1, wherein the at least one
coolant partial stream discharges directly in the outflow channel
for the coolant.
5. The condenser according to claim 1, further comprising a cutoff
arranged in the outflow channel for the coolant stream, the cutoff
essentially separates an area from this outflow channel in which
all or at least most of the partial stream is forced to flow
through the at least one second other flow channel in the second
section and to flow back to the inflow channel.
6. The condenser according to claim 1, wherein the inflow channel,
as viewed in the direction of the inflowing coolant, begins on the
second section, the throttle-like device being arranged relatively
close to the beginning of the inflow channel, the throttle-like
device including at least one vane extending into the inflow
channel, the at least one vane deflects the partial stream into the
at least one other flow channel of the second section.
7. The condenser according to claim 6, wherein the throttle-like
device is arranged roughly at half-height of the second section in
the inflow channel.
8. The condenser according to claim 6, wherein the partial stream
enters the inflow channel again behind the throttle-like device, as
viewed in the direction of the inflowing coolant.
9. The condenser according to claim 1, wherein the inflow channel,
as viewed in the direction of the inflowing coolant, begins on the
first section and the throttle-like device is arranged relatively
close to the end of the inflow channel.
10. The condenser according to claim 5, wherein the throttle-like
device includes a perforated disk.
11. The condenser according to claim 10, further comprising a first
partition arranged in the inflow channel and a second partition
arranged in the outflow channel for the refrigerant.
12. The condenser according to claim 11, wherein the first and
second partitions, the cutoff and the perforated disk lie at
roughly one level and define the barrier between the first and
second sections.
13. The condenser according to claim 1, wherein the throttle-like
device is a cross-sectional narrowing of the inflow channel.
14. The condenser according to claim 11, further comprising a
collecting tank fastened on the stack, the collecting tank takes up
condensed refrigerant coming from the first section, and dispenses
condensed refrigerant into the second section for supercooling.
15. The condenser according to claim 14, wherein one wall of the
collecting tank is formed with a connector having a passage
opening.
16. The condenser according to claim 15, wherein the stack further
includes a first and second cover plate and the connector for
fastening of the collecting tank to the second cover plate, wherein
a spacing is defined between the wall and the second cover
plate.
17. The condenser according to claim 16, wherein the connector
provides a flow connection from the collecting tank through the
second cover plate into the part of the inflow channel separated by
the first partition and into the second section.
18. The condenser according to claim 1, wherein the coolant main
stream, as viewed in the flow direction of the main stream, enters
at least another flow channel of the first section behind the
throttle-like device and flows through it.
Description
CROSS REFERENCE TO RELATED APPLICATIONS
[0001] This application claims priority to German Patent
Application No. DE 10 2013 002 545.1, filed Feb. 14, 2013, the
entire contents of which are hereby incorporated by reference
herein.
BACKGROUND
[0002] The invention relates to a condenser with at least one stack
of heat exchanger plates, which has a first section for
condensation of a refrigerant and a second section for supercooling
of the refrigerant, in which case at least one flow channel for the
refrigerant and at least one other flow channel for a liquid
coolant stream are formed between the heat exchanger plates in each
section, which are in a heat-exchanging relation, the stack being
perforated by inflow and outflow channels for the coolant stream
and for the refrigerant, which are hydraulically connected to at
least one or the other flow channel.
[0003] Such a condenser can be used in air conditioning systems of
vehicles.
[0004] The liquid coolant in U.S. Pat. No. 7,469,554 B2 enters the
second section, flows through it and in so doing supercools the
already condensed refrigerant. The coolant then flows with an
already somewhat increased temperature through the first section in
order to condense the refrigerant.
[0005] It is proposed in DE 10 2011 008 429 A1 to traverse the
first and/or second section with a coolant having a lower
temperature. This permits a performance improvement of the
condenser. However, the system costs are quite high, since a
cooling loop must be equipped accordingly in order to furnish
coolant at a lower temperature.
SUMMARY
[0006] The task of the invention includes a performance improvement
of such condensers without having to equip the coolant loop and
without having to make corresponding investments.
[0007] It is important according to some aspects of the invention
that the coolant stream within the condenser is divisible into a
coolant main stream and at least one coolant partial stream. To
implement this aspect it is further proposed that a throttle-like
device be arranged in the inlet channel for the coolant stream to
divert the partial stream from the coolant entering the condenser.
The partial stream serves for supercooling of the refrigerant in
the second section, i.e., it traverses the at least one other flow
channel of the second section, namely the supercooling section of
the condenser.
[0008] The coolant main stream can enter the at least one other
flow channel of the first section and effectively perform
condensation of the refrigerant without already being significantly
heated beforehand.
[0009] In a variant according to the invention it is proposed that
the partial stream can be fed back to the inlet channel by at least
a second other flow channel in the second section. The partial
stream therefore covers at least a U-shaped path within the second
section or the supercooling section.
[0010] In terms of design it can be advantageous in this context
that a cutoff be arranged in the outflow channel for the coolant
stream, which forces the coolant stream to traverse at least a
second other flow channel in the second section. Instead of cutoff,
another connection could also be provided between the first other
flow channel and the second other flow channel at their ends,
which, however, may be somewhat more cumbersome, since the other
flow channels in this case must not discharge into the outflow
channel.
[0011] Some advantages are expected from this embodiment because
the still relatively cool coolant has a fairly high temperature
difference relative to the refrigerant. Because the partial stream
is fed back to the inlet channel the entire coolant stream can then
flow through the first section and be used for condensation of the
refrigerant.
[0012] According to some embodiments according to the invention,
the partial stream, after traversing the supercooling section and
the at least one other flow channel, discharges directly into the
outflow channel for the coolant stream and leaves the condenser
through it, together with the main stream of the coolant coming
from the first section. Here again there is a higher temperature
difference that can lead to performance improvements.
[0013] The performance improvement of the condenser is expected
without having to provide a low temperature cooling loop. The
system costs will be comparatively low.
[0014] Naturally the condenser according to the invention can also
be installed in cooling systems, for example, in or of vehicles
which are equipped anyway with a low temperature cooling loop for
other reasons. In these cases, at least the direct connection costs
of the condenser can be reduced, since lines from this loop to the
condenser and back again are not required.
[0015] The invention is described with reference to the appended
drawings in three practical examples. This description contains
additional features that might turn out later to be beneficial to
the invention.
[0016] Other aspects of the invention will become apparent by
consideration of the detailed description and accompanying
drawings.
[0017] The appended figures can be understood as sections through a
condenser.
BRIEF DESCRIPTION OF THE DRAWINGS
[0018] FIG. 1 shows a condenser according to the invention with
flow on the refrigerant side.
[0019] FIG. 2 shows the condenser according to FIG. 1 with flow on
the coolant side in a practical example.
[0020] FIG. 3 shows another practical example with flow on the
coolant side.
[0021] FIGS. 4 and 5 show modifications of the practical example
according to FIGS. 1 and 3.
DETAILED DESCRIPTION
[0022] Before any embodiments of the invention are explained in
detail, it is to be understood that the invention is not limited in
its application to the details of construction and the arrangement
of components set forth in the following description or illustrated
in the following drawings. The invention is capable of other
embodiments and of being practiced or of being carried out in
various ways.
[0023] The condenser according to FIGS. 1-5 has a stack of
preferably rectangular heat exchanger plates 1. First and second
cover plates 9, 11 are situated on the stack, which can be seen in
the figures on the left and right side of the stack. The heat
exchanger plates 1 have a peripheral bent edge, which is not shown
in the drawings, and a generally flat bottom, which, however, can
also have local structures to generate turbulence. The individual
plates 1 lie against each other on this edge so that flow channels
2 for a refrigerant RF and flow channels 3 for a liquid coolant
stream KM remain between their bottoms, in which heat exchange
mostly occurs. In the practical examples another flow channel 3 for
coolant therefore follows the flow channel 2 for refrigerant, i.e.,
the channels 2, 3 alternate, as can be seen from the figures. The
flow channels 2 for refrigerant RF are shown with dashed lines.
Inserted turbulizers (fins or the like) can also be arranged in the
flow channels 2, 3 (not shown).
[0024] An inflow channel 4 for refrigerant RF, which is formed by
means of openings in plates 1 and extends through the plate stack,
is connected via the flow channels 2 to an outflow channel 5 for
refrigerant also extending through the plate stack (FIG. 1).
Likewise, another inflow channel 6 for the coolant stream is
connected via flow channels 3 to the outflow channel 7 for the
coolant (FIGS. 2-5). The openings that form the inflow and outflow
flow channels 4-7 are arranged in the corner areas of the plates
1.
[0025] Corresponding connectors 21 are soldered to the cover plates
9, 11 on the inflow channel 6 for coolant KM and on the outflow
channel 7. Other connections 22 are provided for refrigerant RF on
the inflow and outflow channels 4, 5.
[0026] As is also apparent from FIG. 1, a collecting tank 30 is
fastened on the stack, more precisely stated, on its second cover
plate 11, which takes up the condensed refrigerant coming from the
first section 10 through a refrigerant line 32 and which flows from
the collecting tank 30 into the second section 20 for supercooling.
The collecting tank 30 causes any gas bubbles still present in
refrigerant RF to be separated and only liquid refrigerant can
reach the second section 20. It can also contain a dryer (not
shown). The collecting tank 30 is equipped with a connector 31
having at least one passage opening, through which the liquid
refrigerant RF can flow into the second section 20. The connector
31 is situated on the opposite end of the mentioned inlet channel 4
on the second cover plate 11. The refrigerant encounters a
partition 14 or section separation in the inlet channel 4 mentioned
further below and then flows into the second section 20. It leaves
the second section 20 via the outflow channel 5, in which a
partition 14 is also situated, and flows through another connection
22 back into circulation (not shown). The connector 31 is
simultaneously formed as a solder connector 31 in order to permit
the mentioned fastening. The solder connector 31 ensures a slight
spacing 33 between the other wall of the collecting tank 30 and
cover plate 11, which has manufacturing advantages.
[0027] With the practical example according to FIG. 2, a situation
is achieved in which a partial stream KMT of liquid coolant also
arrives in the second section 20, or in the supercooling section
with a fairly low temperature, although the beginning of the inflow
channel 6 is situated on the first section 10 which is the
condensation section. This is made possible by the fact that a
throttle-like device in the form of a perforated disk 8b is
arranged within the condenser close to the end of the inlet channel
6, namely at the transition from the first 10 to the second section
20. The position of the perforated disk 8b hydraulically separates
two flow channels 3 for coolant from the stack in this practical
example, which together with two other flow channels 2 for
refrigerant RF form the second section 20. The coolant stream KMT
flows through the two flow channels 3 and discharges directly into
outflow channel 7. A coolant main stream can enter the flow
channels 3 of the first section 10 in front of the perforated disk
8b with low temperature -viewed in its direction of flow.
[0028] The two flow channels 2 for refrigerant RF are then
separated by means of the mentioned partitions 14, viewed
hydraulically, from the stack, which are situated in corresponding
positions in the inflow and outflow channels 4, 5 for refrigerant,
as is readily apparent from FIG. 1.
[0029] The practical examples according to FIGS. 3-5 can result in
larger thermodynamic advantages. In these practical examples, the
beginning of the inflow channel 6 (in contrast to FIG. 2) is
situated on the second section 20 or on the supercooling section.
Relatively close to the mentioned beginning, namely in the area of
the second section 20, another throttle-like device is arranged in
the inflow channel 6, i.e., within the condenser in the form of a
vane 8a or the like, extending into the inflow channel 6. The vane
8a is designed somewhat curved in the direction of the arriving
coolant in order to equip it with guiding properties to divert the
coolant partial stream KMT from the coolant. The partial stream KMT
can be adjusted by the size of vane 8a, which extends into the
inflow channel 6, starting at the mentioned flow channel 3. In FIG.
3 the vane 8a is situated in the position in which it provides a
single flow channel 3, in which the coolant stream KMT flows to the
outflow channel 7, and an additional flow channel 3a, in which the
partial stream KMT flows back to the inflow channel 6 in the second
section 20. For this purpose a full cutoff 12a is arranged in the
outflow channel 7, which causes a reversal of the direction of
flow.
[0030] FIGS. 4 and 5 differ from FIG. 3 by an altered position of
the vane 8a and cutoff 12a. In these figures the positions were
chosen so that two flow channels 3 are present for inflow of the
partial stream KMT and two additional flow channels 3a for its
backflow.
[0031] Generally speaking, the vane 8a is always situated roughly
at half-height h of the second section 20. Cutoff 12a is situated,
on the other hand, in a position that corresponds to roughly height
h of the second section 20. Height h in the drawings corresponds
roughly to the plate area shown by the braces and the reference
number 20 (see FIGS. 3 and 5).
[0032] In contrast to FIGS. 3 and 4, the cutoff 12b in FIG. 5 is
designed as a partial cutoff 12b. In the illustrated case, the
partial cutoff 12b is provided by the fact that cutoff 12a is
provided with a central hole 13. Through corresponding hole sizes
the flow through the second section 20 can be optimized by means of
partial stream KMT, which also applies to the perforated disk 8b,
which was discussed in conjunction with FIG. 2 above.
[0033] The coolant main stream in the practical examples (viewed in
its flow direction) enters the flow channels 3 of the first section
10 with even lower temperature beyond the throttle-like device
8a.
[0034] It is also possible to split off the coolant partial stream
KMT outside the condenser but preferably in its immediate vicinity
from the coolant stream KM and to feed it separately into the
second section 20, which was not shown. Flow through the condenser
by means of the main stream and partial stream KMT then remains
unchanged.
[0035] Finally, it should be mentioned that the condenser can be
also traversed meander-like by arranging additional cutoffs 12 and
partitions 14 in the inflow and outflow channels 4-7 in the first
and second sections 10, 20, so that it has corresponding
subsections. The arrows in the figures of the practical examples,
on the other hand, show that only simple flow and in the second
section 20, preferably also, U-shaped flow are provided.
[0036] In condensers that use air as coolant and which ordinarily
have plate stacks that do not form flow channels, but a tube-rib
stack, a meander-like flow can also occur on the refrigerant side
in one or both sections 10, 20. The ribs represent flow channels
for the cooling air and the tubes are flow channels for the
refrigerant RF. The partitions 14 forming the mentioned subsections
for deflection of the refrigerant are situated in collecting tubes
arranged on the tube ends.
[0037] Various features and advantages of the invention are set
forth in the following claims.
* * * * *