U.S. patent application number 14/429944 was filed with the patent office on 2015-08-13 for condenser.
This patent application is currently assigned to MAHLE INTERNATIONAL GMBH. The applicant listed for this patent is MAHLE INTERNATIONAL GMBH. Invention is credited to Herbert Hofmann, Stefan Schmidgall, Sascha Unger.
Application Number | 20150226469 14/429944 |
Document ID | / |
Family ID | 50235315 |
Filed Date | 2015-08-13 |
United States Patent
Application |
20150226469 |
Kind Code |
A1 |
Hofmann; Herbert ; et
al. |
August 13, 2015 |
CONDENSER
Abstract
The invention relates to a condenser in stacked-plate design,
wherein a heat exchanger block is formed by a plurality of plate
elements, which form channels adjacent to each other between the
plate elements when the plate elements are stacked on top of each
other, wherein a first number of the channels is associated with a
first flow channel and a second number of the channels is
associated with a second flow channel, and a refrigerant can flow
through the first flow channel and a coolant can flow through the
second flow channel, wherein the first flow channel has a first
region for desuperheating and condensing the vaporous refrigerant
and a second region for subcooling the condensed refrigerant.
Inventors: |
Hofmann; Herbert;
(Stuttgart, DE) ; Schmidgall; Stefan; (Stuttgart,
DE) ; Unger; Sascha; (Ludwigsburg, DE) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
MAHLE INTERNATIONAL GMBH |
Stuttgart |
|
DE |
|
|
Assignee: |
MAHLE INTERNATIONAL GMBH
Stuttgart
DE
|
Family ID: |
50235315 |
Appl. No.: |
14/429944 |
Filed: |
September 2, 2013 |
PCT Filed: |
September 2, 2013 |
PCT NO: |
PCT/EP2013/068118 |
371 Date: |
March 20, 2015 |
Current U.S.
Class: |
62/506 ; 165/143;
165/166 |
Current CPC
Class: |
F28D 2021/0084 20130101;
F28F 9/26 20130101; F25B 2339/043 20130101; F28F 2270/00 20130101;
F28D 9/0075 20130101; F25B 39/04 20130101; F25B 2339/044 20130101;
F28D 9/00 20130101; F28D 9/0056 20130101 |
International
Class: |
F25B 39/04 20060101
F25B039/04; F28F 9/26 20060101 F28F009/26; F28D 9/00 20060101
F28D009/00 |
Foreign Application Data
Date |
Code |
Application Number |
Sep 21, 2012 |
DE |
20 2012 010 732.1 |
Nov 12, 2012 |
DE |
10 2012 220 594.2 |
Claims
1. A condenser in stacked-plate construction, wherein a heat
exchanger block is formed of a plurality of plate elements, which,
stacked one on top of another, form mutually adjacent channels
between the plate elements, wherein a first number of the channels
is assigned to a first flow channel and a second number of the
channels is assigned to a second flow channel, and a refrigerant is
flowable through the first flow channel and a coolant is flowable
through the second flow channel, wherein the first flow channel has
a first region for the desuperheating and condensation of the
vaporous refrigerant and a second region for the supercooling of
the condensed refrigerant, wherein at least a portion of the first
flow channel is in thermal contact with at least a portion of the
second flow channel, and the first region has a first fluid supply
line and a first fluid discharge line and the second region has a
second fluid supply line and a second fluid discharge line, wherein
the condenser has a receiver for storing the refrigerant, and a
refrigerant crossover from the first region into the second region
leads through the receiver , wherein the receiver is in fluid
communication with the first region via the first fluid discharge
line, which also forms the fluid inlet of the receiver, and is in
fluid communication with the second region via the second fluid
supply line, which also forms the fluid outlet of the receiver,
wherein the receiver is disposed on an outer surface of the
condenser.
2. The condenser as claimed in claim 1, wherein the coolant in the
second flow channel and the refrigerant in the first flow channel
are flowable in cocurrent flow to each other and/or in
countercurrent flow to each other.
3. The condenser as claimed in claim 1, wherein the first fluid
discharge line and/or the second fluid supply line are/is disposed
inside and/or outside the heat exchanger block.
4. The condenser as claimed in claim 1, wherein the first fluid
discharge line and/or the second fluid supply line are/is formed by
a pipeline.
5. The condenser as claimed in claim 1, wherein the first fluid
supply line and the second fluid supply line viewed along the
principal direction of flow through a channel between the plate
elements, are disposed at the same end region of the condenser,
wherein the first fluid discharge line and the second fluid
discharge line are disposed at the opposite end region of the
condenser.
6. The condenser as claimed in claim 5, wherein the first fluid
supply line and the second fluid supply line are disposed, in the
final assembly position of the condenser, at the upper end region
of the condenser.
7. The condenser as claimed in claim 1, wherein the internal volume
share of the second region of the first flow channel represents
maximally about 40%, here preferably about 20%, here preferably
between about 5% and about 15% of the internal total volume of the
first flow channel.
8. The condenser as claimed in claim 1, wherein the coolant supply
line and the coolant discharge line of the second flow channel,
viewed along the direction of flow through a channel between the
plate elements, are disposed at opposite end regions of the
condenser.
9. The condenser as claimed in claim 1, wherein the first region
and/or the second region of the first flow channel inside the
condenser are/is diverted one or more times in their/its principal
direction of flow.
10. The condenser as claimed in claim 1, wherein the second flow
channel inside the condenser is diverted at least once in its
principal direction of flow through around 180.degree..
11. The condenser as claimed in claim 1, wherein the second flow
channel is diverted once in its principal direction of flow through
around 180.degree., whereby a forward flow region and a return flow
region are formed, wherein the internal volume of the forward flow
region of the second flow channel and the internal volume of the
return flow region of the second flow channel are approximately
equal in size and/or unequal in size.
12. The condenser as claimed in claim 11, wherein the coolant flows
through the second flow channel in such a way that, along the
principal direction of flow through the second flow channel, it
first enters into thermal contact with the second region of the
first flow channel or it first enters into thermal contact with the
second region and at least a portion of the first region of the
first flow channel and, respectively after the diversion, enters
substantially into thermal contact with the first region of the
first flow channel.
13. The condenser as claimed in claim 1, wherein a thermal
separation is present between the first region for the
desuperheating and condensation of the vaporous refrigerant and the
second region for the supercooling of the condensed
refrigerant.
14. The condenser as claimed in claim 13, wherein the thermal
separation is configured as a thermally insulating plate, as an air
gap, as an air-conducting channel, as a part of the second flow
channel having a multiple coolant path and/or as a part of the
second flow channel having a larger flow cross-sectional area than
the rest of the second flow channel.
Description
TECHNICAL FIELD
[0001] The invention relates to a condenser in stacked-plate
construction, wherein a heat exchanger block is formed of a
plurality of plate elements, which, stacked one on top of another,
form mutually adjacent channels between the plate elements, wherein
a first number of the channels is assigned to a first flow channel
and a second number of the channels is assigned to a second flow
channel, and a refrigerant is flowable through the first flow
channel and a coolant is flowable through the second flow channel,
wherein the first flow channel has a first region for the
desuperheating and condensation of the vaporous refrigerant and a
second region for the supercooling of the condensed
refrigerant.
PRIOR ART
[0002] In refrigerant circuits of air conditioning systems for
motor vehicles, condensers are used to cool the refrigerant to the
condensation temperature and subsequently condense the refrigerant.
Condensers regularly have a receiver in which a refrigerant volume
is held to compensate volume fluctuations in the refrigerant
circuit. Moreover, as a result of the holding of the refrigerant in
the receiver, a stable supercooling of the refrigerant is
achieved.
[0003] Often, additional means for drying and/or filtering the
refrigerant are provided in the receiver. The receiver is generally
disposed on the condenser. It is flowed through by the refrigerant,
which has already flowed through a portion of the condenser. After
having flowed through the receiver, the refrigerant is led back
into the condenser and supercooled in a supercooling section to
below the condensation temperature.
[0004] In conventional condensers in fin-tube construction, the
refrigerant for these is led out of the condenser from one of the
collecting tubes disposed at the side of a tube-fin block, and led
into the receiver.
[0005] In condensers which are built in stacked-plate construction,
possibilities for adding the receiver to the condenser as an
additional layer of plate elements are known in the prior art.
[0006] It is additionally known to lead the refrigerant via a
special distributor plate out of the condenser built in
stacked-plate construction and feed it to an external receiver, and
to return the refrigerant after the receiver back into the
condenser.
[0007] Furthermore, US 20090071189 A1 discloses a condenser in
stacked-plate construction, in which a first stack of plate
elements constitutes a first cooling and condensation region and a
second stack of plate elements constitutes a supercooling region.
The first stack is separated from the second stack by a housing,
which contains a receiver and a dryer.
[0008] A drawback with the devices of the prior art is that the
integration of condensers in stacked-plate construction, receivers
and supercoolers is hitherto achieved in a very elaborate manner.
In addition to a complex structure, the condensers from the prior
art are distinguished by an elevated production complexity. This
gives rise to additional costs in terms of using the condensers,
which make their use unattractive.
REPRESENTATION OF THE INVENTION, OBJECT, ACHIEVEMENT,
ADVANTAGES
[0009] The object of the present invention is therefore to provide
a condenser which is suitable for condensing a refrigerant,
supplying it and, furthermore, supercooling it, wherein the
condenser is characterized by a simple structure and a compact
construction and is economical to produce.
[0010] The object of the present invention is achieved by a
condenser in stacked-plate construction having the features of
claim 1.
[0011] An illustrative embodiment of invention relates to a
condenser in stacked-plate construction, wherein a heat exchanger
block is formed of a plurality of plate elements, which, stacked
one on top of another, form mutually adjacent channels between the
plate elements, wherein a first number of the channels is assigned
to a first flow channel and a second number of the channels is
assigned to a second flow channel, and a refrigerant is flowable
through the first flow channel and a coolant is flowable through
the second flow channel, wherein the first flow channel has a first
region for the desuperheating and condensation of the vaporous
refrigerant and a second region for the supercooling of the
condensed refrigerant, wherein at least a portion of the first flow
channel is in thermal contact with at least a portion of the second
flow channel, and the first region has a first fluid supply line
and a first fluid discharge line and the second region has a second
fluid supply line and a second fluid discharge line, wherein the
condenser has a receiver for storing the refrigerant, and a
refrigerant crossover from the first region into the second region
leads through the receiver, wherein the receiver is in fluid
communication with the first region via the first fluid discharge
line, which also forms the fluid inlet of the receiver, and is in
fluid communication with the second region via the second fluid
supply line, which also forms the fluid outlet of the receiver,
wherein the receiver is disposed on an outer surface of the
condenser.
[0012] A condenser in stacked-plate construction is particularly
compact and can therefore also be accommodated on a small
installation space. A good thermal contact between the first flow
channel and the second flow channel is particularly advantageous in
order that the heat transfer between the fluids is as efficient as
possible. The arrangement of the receiver as close as possible to
the condenser or on the heat exchanger block of the condenser has
the advantage that only short distances have to be negotiated by
means of fluid lines. The thermal deficiencies, such as, for
instance, the heating of the coolant or refrigerant by surrounding
heat sources, as well as the negative effects on the pressure loss
inside the condenser, can therefore be minimized.
[0013] In addition, it can be advantageous if the coolant in the
second flow channel and the refrigerant in the first flow channel
are flowable in cocurrent flow to each other and/or in
countercurrent flow to each other.
[0014] A flowing of the coolant and of the refrigerant in
countercurrent flow allows the maximally transferable heat quantity
to be increased, which helps to boost the efficiency of the
condenser. On the other hand, a flowing in cocurrent flow can be
realized particularly easily.
[0015] It can also be expedient if the first fluid discharge line
and/or the fluid supply line are/is disposed inside and/or outside
the heat exchanger block.
[0016] Depending on the position of the receiver, it is expedient
if the first fluid discharge line, which also simultaneously
constitutes the supply line to the receiver, and the second fluid
supply line, which also simultaneously constitutes the discharge
line from the receiver, run inside or outside the condenser. The
running of the lines outside the condenser is easier to realize,
since the installation space is less heavily restricted and the
shaping limits of the individual plate elements do not have to be
taken into account.
[0017] In advantageous embodiments, the lines can also run disposed
on the outer plate elements. This can be done, for example, through
channels integrated in the plate elements.
[0018] In addition, it can be particularly advantageous if the
first fluid discharge line and/or the second fluid supply line
are/is formed by a pipeline.
[0019] A pipeline offers the advantage of very great freedom of
design for the routing and arrangement of the line. As a result of
pipelines, even complex line routings can be realized.
[0020] It is also preferable if the first fluid supply line and the
second fluid supply line, viewed along the principal direction of
flow through a channel between the plate elements, are disposed at
the same end region of the condenser, wherein the first fluid
discharge line and the second fluid discharge line are disposed at
the opposite end region of the condenser.
[0021] As a result of an arrangement of the first and the second
fluid supply line at a common end region of the condenser and of
the first and the second fluid discharge line at the opposite end
region of the condenser, a guidance of the fluid flows in
countercurrent flow inside the condenser can be realized in a
particularly simple manner.
[0022] In a particularly favorable embodiment of the invention, it
is provided, moreover, that the first fluid supply line and the
second fluid supply line are disposed, in the final assembly
position of the condenser, at the upper end region of the
condenser.
[0023] The feeding of the fluid at the, in the final assembly
position, upper end region of the condenser is particularly
advantageous, since, in this way, the flow inside the condenser is
additionally supported by the weight force of the fluid. In
addition, the generated pressure loss inside the condenser is less
than if the fluid has to be transported upward counter to the
weight force.
[0024] In an alternative embodiment of the invention, it can be
provided that the internal volume share of the second region of the
first flow channel represents maximally about 40%, here preferably
about 20%, here preferably between about 5% and about 15% of the
internal total volume of the first flow channel.
[0025] Thermally, is advantageous if the supercooling section,
which corresponds to the second region of the first flow channel,
takes up as large a volume share as possible of the total volume o
the first flow channel, since the fluid temperature at the
condenser outlet can thereby be kept particularly low. This can
lead to an improvement in the system performance.
[0026] However, as a result of the reduction of the heat
transmission surface in the condensation region, which corresponds
to the first region of the first flow channel, the heat
transmission is worsened. This impacts negatively on the pressure
on the high pressure side crone refrigerant circuit, which, all in
all, leads to a poorer system performance.
[0027] A limitation of the supercooling section to the above-stated
volume shares is therefore advantageous with a view to the
efficiency of the condenser.
[0028] Furthermore, it is preferable if the coolant supply line and
the coolant discharge line of the second flow channel, viewed along
the direction of flow through a channel between the plate elements,
are disposed at opposite end regions of the condenser.
[0029] The arrangement of the coolant supply line and of the
coolant discharge line at opposite end regions of the condenser is
Particularly advantageous if the-coolant is intended to flow
through the condenser without substantial diversion.
[0030] According to a particularly preferred refinement of the
invention, it can be provided that the first region and/or the
second region of the first flow channel inside the condenser are/is
diverted one or more times in their/its principal direction of
flow.
[0031] Through a single or multiple diversion of the flow
direction, the effect can be achieved that the refrigerant and the
coolant flow either in cocurrent flow or in countercurrent flow to
each other. The heat transfer between coolant and refrigerant can
thereby be influenced.
[0032] Moreover, it can be advantageous if the second flow channel
inside the condenser is diverted at least once in its principal
direction of flow through around 180.degree..
[0033] A diversion of the second flow channel can be advantageous
in order to bring the flowing coolant into cocurrent flow or
countercurrent flow with the refrigerant. The heat transfer between
refrigerant and coolant can be influenced by a diversion of the
second flow channel.
[0034] A further preferred illustrative embodiment is characterized
in that the second flow channel is diverted once in its principal
direction of flow through around 180.degree., whereby a forward
flow region and a return flow region are formed, wherein the
internal volume of the forward flow region of the second flow
channel and the internal volume of the return flow region of the
second flow channel are approximately equal in size and/or unequal
in size.
[0035] The forward flow region of the second flow channel and the
return flow region can advantageously be approximately equal in
size in terms of their volume. This is particularly advantageous,
in particular with respect to the generated pressure losses.
[0036] Where the separation into forward flow region and return
flow region is geared to the division into condensation region and
supercooling region, an unequal distribution can also, however, be
advantageous.
[0037] It is additionally advantageous if the coolant flows through
the second flow channel in such a way that, along the principal
direction of flow through the second flow channel, it first enters
into thermal contact with the second region of the first flow
channel or it first enters into thermal contact with the second
region and at least a portion of the first region of the first flow
channel and, respectively after the diversion, enters substantially
into thermal contact with the first region of the first flow
channel.
[0038] An influx of the coolant such that essentially a thermal
contact first takes place between the second region of the second
flow channel and the coolant allows the output temperature of the
refrigerant from the condenser to be effectively reduced. The
coolant which flows freshly into the condenser has its lowest
temperature directly at the fluid inlet. As a result, the heat
transfer is particularly high. In order to avoid an unnecessarily
high pressure loss due to the unequal volume shares between the
first region and the second region of the first flow channel for
the coolant, the coolant, in addition to the thermal contact with
the second region, can also be brought into thermal contact with a
portion of the first region of the first flow channel. In this way,
the forward flow section and the return flow section of the coolant
are designed such that an approximately equal internal volume is
present, whereby the internal pressure loss is reduced.
[0039] Furthermore, it is expedient if a thermal separation is
present between the first region for the desuperheating and
condensation of the vaporous refrigerant and the second region for
the supercooling of the condensed refrigerant.
[0040] As a result of a thermal separation between the condensation
region and the supercooling region of the condenser, a thermal
interaction between the fluids in the supercooling region and in
the condensation region can be achieved. In particular, a renewed
warming of the refrigerant can be avoided, which can end up
boosting the system performance of the condenser.
[0041] In an alternative embodiment of the invention, it can be
provided that the thermal separation is configured as a thermally
insulating plate, as an air gap, as an air-conducting channel, as a
part of the second flow channel having a multiple coolant path
and/or as a part of the second flow channel having a larger flow
cross-sectional area than the rest of the second flow channel.
[0042] Advantageously, the thermal separation can be realized by
one of the plate elements of the condenser, whereby the design
complexity is kept to a minimum. On the other hand, specially
produced plate elements can lead to a stronger thermal
separation.
[0043] Advantageous refinements of the present invention are
described in the subclaims and the following description of the
figures.
BRIEF DESCRIPTION OF THE DRAWINGS
[0044] The invention is explained in detail on the basis of
illustrative embodiments with reference to the drawings,
wherein:
[0045] FIG. 1 shows a perspective view of a condenser in
stacked-plate arrangement, having a receiver disposed on the
outside of the housing,
[0046] FIG. 2 shows a further view of the condenser of FIG. 1,
wherein particularly the line from the receiver to the rear side of
the condenser and the discharge line of the refrigerant from the
condenser can be seen,
[0047] FIG. 3 shows a schematic representation of a condenser in
stacked-plate construction having an externally arranged receiver,
wherein the coolant and the refrigerant flow in countercurrent flow
to each other in the condensation region and in cocurrent flow to
each other in the supercooling region,
[0048] FIG. 4 shows a further schematic view of a condenser,
wherein the coolant and the refrigerant flow in countercurrent flow
to each other both in the condensation region and in the
supercooling region,
[0049] FIG. 5 shows a further schematic view of a condenser,
wherein the coolant is diverted inside the condenser and, as a
result, inside the condenser are formed regions in which the
coolant and the refrigerant flow both in cocurrent flow and in
countercurrent flow to each other, wherein the refrigerant is
transported through the supercooling region out of the condensation
region into the receiver, and
[0050] FIG. 6 shows a further schematic view of a condenser,
wherein a thermal separation is introduced between the condensation
region and the supercooling region by a double coolant path.
PREFERRED EMBODIMENT OF THE INVENTION
[0051] FIG. 1 shows a perspective view of a condenser 1 in
stacked-plate construction. The condenser 1 here consists of a
plurality of individual plate elements, which, stacked one on top
of another, form the heat exchanger block 7. The heat exchanger
block 7 is designed in its interior such that a plurality of
channels are created between the individual plate elements. A
number of these channels is assigned to a first channel, which can
be flowed through by a refrigerant. A further number of the
channels is assigned to a second flow channel, which can be flowed
through by a coolant. Inside the heat exchanger block 7, the first
flow channel is at least partially in thermal contact with the
second flow channel, so that a heat transfer can take place between
the first flow channel and the second flow channel.
[0052] By using various embodiments of the plate elements, the
effect can be achieved that, inside the neat exchanger block 7, a
plurality of flow paths for the first and second flow channel
respectively are formed. The fluid flowing through the first flow
channel and second flow channel respectively can be diverted
through the different flow paths inside the heat exchanger block 7
and can thus in total cover a longer flow path inside the condenser
I.
[0053] On an outer surface of the heat exchanger block 7 is
disposed a receiver 2. This receiver serves to supply the
refrigerant which flows along the first flow channel. By means of
the receiver 2, a volume fluctuation of the refrigerant inside the
condenser and the rest of the refrigerant circuit can be
compensated. In advantageous embodiments, the receiver 2 can have
means for drying and filtering the refrigerant.
[0054] The receiver 2 shown in FIG. 1 has a cylindrical housing and
is disposed on the outer side of the heat exchanger block 7 In
alternative embodiments, the receiver 2 can also have other
configurations. The representation of the receiver 2 is
exemplary.
[0055] The receiver 2 is connected by receiver connections 8 to the
first flow channel inside the condenser 1 and is in fluid
communication therewith.
[0056] Furthermore, the condenser 1 has a refrigerant inlet 3 at
its upper left-hand end region. At the upper right-hand end region,
the condenser 1 has a coolant outlet 6. At the lower right-hand end
region, the condenser 1 has a coolant inlet 5.
[0057] A refrigerant can in this way flow is the refrigerant inlet
3 into the first flow channel of the heat exchanger block 7 and be
distributed through the channels which are assigned to the first
flow channel. From the first flow channel 1, the refrigerant then
flows via the receiver connections 8 into the receiver 2. From the
receiver 2, the refrigerant flows back into the heat exchanger
block 7 and is distributed onward through the first flow channel of
the heat exchanger block 7. Finally, the refrigerant flows via the
refrigerant outlet 4, which is disposed on the rear side (facing
away from the viewer) of the condenser 1, out of the heat exchanger
block 7 of the condenser 1.
[0058] The coolant flows through the coolant inlet 5 into the
second flow channel of the heat exchanger block 7 and is
distributed along this flow channel in the heat exchanger block and
eventually flows out of the condenser through the coolant outlet
G.
[0059] The first flow channel is split into a first region and a
second region. The first region extends from the refrigerant inlet
3 up to the transition into the receiver 2. The second region of
the first flow channel extends from the outlet of the receiver 2 up
to the refrigerant outlet 4 of the condenser 1. The coolant which
flows through the second flow channel is in thermal contact both
with the first region and with the second region of the first flow
channel, whereby a heat transfer comes about.
[0060] FIG. 2 shows a rear view of the condenser I of FIG. 1. In
particular, the pipeline 10 and the fluid outlet 4 can be seen. The
pipeline 10 here constitutes the fluid line, which runs back from
the outlet of the receiver to the heat exchanger block 7 and leads
the refrigerant back between the plate elements.
[0061] FIG. 3 shows a schematic view of a condenser 20. A possible
embodiment of the condenser of FIGS. 3 to 5 is shown in FIGS. 1 and
2. The routings of the outer pipelines and the arrangement of the
receiver can here differ from the examples shown in FIGS. 1 and 2.
Similarly the number of plate elements used and the arrangement of
the individual fluid inlets and fluid outlets on the heat exchanger
block.
[0062] The condenser 20 shown in FIG. 3 has an externally arranged
receiver 21.
[0063] The coolant supply line to the condenser 20 is represented
with the reference symbol 27. The coolant discharge line of the
condenser 20 is represented with the reference symbol 28. The
coolant flows along the flow paths 31, 32 along the already
previously discussed second flow channel through the condenser 20.
In FIG. 3, the coolant flows without diversion both through the
first region of the first flow channel, which constitutes a
condensation region 34, and through the second region of the first
flow channel, which constitutes a supercooling region 35.
[0064] The condensation region 34 is dimensioned larger in relation
to the supercooling region 35 and, in proportion to the total
volume of the first flow channel 1, takes up a larger share.
[0065] In order to ensure optimal working of a condenser in
general, every effort must be made to ensure that the ratio between
the condensation region and the supercooling region is in a certain
maximal mutual relationship. It is therefore advisable that the
internal volume of the first flow channel assigned to the
supercooling region, in relation to the internal volume of the
first flow channel assigned to the condensation surface, is no
greater than 40% of the total internal volume of the first now
channel. Advantageously, every effort must be made to ensure that
the internal volume of the first flow channel assigned to the
supercooling region even becomes no greater than 20%, a division of
the total internal volume of the first flow channel into about 5%
to 15% of the volume for the supercooling section and 85% to 95% of
the internal volume for the condensation region being optimal.
[0066] To the condenser 20 of FIG. 3, a refrigerant is fed via the
first fluid supply line 23 into the condensation region 34. There
it flows downward, distributed over the individual channels of the
condensation region 34, and passes via the first fluid discharge
line 24 into the receiver 21. From the receiver 21, the now fully
condensed refrigerant is led along the fluid line 33, via the
second fluid supply line 25, into the supercooling region 35. The
discharge of the refrigerant from the condensation region 34, and
the feed into the supercooling region 35, here take
[0067] Place at the lower end region of the condenser 20. The place
then flows upward in the supercooling region 35 and flows out of
the condenser 20 via the second fluid discharge line 26.
[0068] The flow path of the refrigerant inside the condenser is
represented via the arrows bearing the reference symbols 29 and 30.
The arrows bearing the reference symbols 31 and constitute the flow
path of the coolant inside the condenser 20. It can be seen that
the coolant flows in countercurrent flow to the refrigerant in the
condensation region 34 and in cocurrent flow in the supercooling
region 35. By reversing the direction of flow of the coolant, a
reversal of these relationships is also achievable.
[0069] In FIG. 3 is represented a condenser 20 in which, both
inside the condenser region 34 and inside the supercooling region
35, no separate diversion of the coolant or of the refrigerant
takes place.
[0070] FIG. 4 shows an alternative embodiment of a condenser 40.
The-condenser 40 has a heat exchanger block 42, which, as described
in FIGS. 1 and 2, consists of a plurality of plate elements. On the
exterior of the condenser 40 is disposed a receiver 41, which is in
fluid communication with the condenser 42. As also in FIG. 3 the
coolant, is streamed substantially without diversion, along its
principal direction of flow, through the condenser 40. The coolant
supply line 47 is disposed on the lower region of the condenser 40.
The coolant discharge line 48 is disposed at the upper region of
the condenser 40.
[0071] In all FIGS. 3 to 5, the positioning both of the fluid
supply line and of the fluid discharge line both for the coolant
and for the refrigerant, is merely indicated. The schematic
representation is not capable of representing the precise
positioning of the supply lines and discharge lines on the outer
surfaces of the condensers. The supply lines and discharge lines
can be disposed primarily on the end faces of the condenser, which
are created by the respectively topmost and bottommost plate
element of the heat exchanger block. A feed on the side faces of
the plate elements is very complex in design terms and only
conditionally possible. The feeding of the fluids into the
individual channels inside the condenser can be effected in a wide
variety of ways through the structural design of the individual
plate elements.
[0072] The fluid can be led, for instance, directly into the first
channel, which is created between the first and the second plate
element. Alternatively, the fluid can be led between the plate
elements, for instance, also by a closure of individual plate
elements or by the insertion of an immersion cane into any other
channel. The possibilities for dividing the individual channels
into the first flow channel and the second flow channel inside the
condenser substantially correspond to those which are already known
in the prior art.
[0073] In FIG. 4, the refrigerant flows via the first fluid supply
line 43 in the upper region of the condenser 40 into the
condensation region 54. It flows downward along the flow path 49 in
the condensation region and flows via the first fluid discharge
line 44 over into the receiver 41. From the receiver 41, the fully
condensed refrigerant is led via the fluid line 53 to the second
fluid supply line 45, which, in contrast to FIG. 3, is now disposed
in the upper region of the condenser 40 on the side of the
supercooling section 55. The refrigerant then flows downward along
the flow path 50 in the supercooling region 55 of the condenser and
eventually flows out of the condenser via the second fluid
discharge line 46.
[0074] As a result of the non-diverted flow of the coolant from
bottom to top through the condenser 40 and the feed of the
refrigerant in the upper region of the condenser 40, the coolant is
in countercurrent flow with the refrigerant both in the
condensation region 54 and in the supercooling region 55.
[0075] By reversing the flow-through direction of the coolant, the
effect can be achieved that, both in the condensation region 54 and
in the supercooling region 55, the refrigerant flows in cocurrent
flow with the coolant. In order to produce a higher heat transfer
between the refrigerant and the coolant, a layout according to FIG.
4 is, however, preferable.
[0076] FIG. 5 shows a further embodiment of a condenser 60. The
condenser 60 has a heat exchanger block 62, which, as already
previously described, is formed of the individual plate elements.
In addition, the condenser 60 has a condensation region 81 and a
supercooling region 82. In contrast to the preceding FIGS. 3 and 4,
the condensation region 81 is now divided into a plurality of flow
paths 79, 80. In the representation of FIG. 5, the condensation
region 81 is formed of the flow path 79 and the flow path 80. The
supercooling region 82 is formed of the flow path 77. Between the
flow path 80 and the flow path 79, the refrigerant undergoes a
diversion through around 180.degree.. Each of the flow paths 77, 79
and 80 of the condenser region 81 and of the supercooling region 82
can consist of one or more channels of the first flow channel.
[0077] In alternative embodiments, a division both of the
condensation region and of the supercooling region into a differing
number of flow paths is also conceivable. The division of the
condensation region 81 into two flow paths 79, 80 here serves for
better representation. In order to maintain a through-flow
principle analogous to FIG. 5, it is advantageous, however, if the
number of the flow paths in the condensation region 81 is even and
in the supercooling region 82 is odd.
[0078] Outside the condenser 60 is disposed a receiver 61, through
which the refrigerant flows. At variance with FIGS. 3 and 4, the
coolant is not now led without diversion through the condenser, but
undergoes inside the condenser 60 a 180.degree. diversion, whereby
a forward flow section and return flow section is formed in the
condenser.
[0079] The coolant is led via the coolant supply line 67 into the
upper region of the condenser 60 and diverted in the lower region
of the condenser 60 so as subsequently to flow on upward and flow
out of the condenser 60 via the coolant discharge line 68. In order
to realize this diversion, those channels inside the heat exchanger
block 62 which are assigned to the second flow channel are mutually
assigned via the structural design of the respective plate elements
such that the coolant in one portion of the second flow channel can
flow out of the upper region into the lower region of the condenser
60. There it flows over into the rest of the second flow channel
and along the channels of the second flow channel back into the
upper region of the condenser.
[0080] In the representation shown in FIG. 5, the forward flow
section of the coolant extends to the channels of the second flow
channel which are in direct thermal exchange with the supercooling
region 82 of the first flow channel, and to a number of channels of
the second flow channel which are in thermal contact with the
condensation region 81 of the first flow channel. The return flow
section of the coolant is limited to those channels of the second
flow channel which are in direct thermal exchange with the
condensation region 81 of the first flow channel. A differing
division can similarly be provided.
[0081] In order to achieve an even as possible pressure loss both
in the forward flow section and in the return flow section of the
coolant, it is advantageous if the channels which in total form the
second flow channel are assigned approximately to same parts of the
forward flow section and of the return flow section of the
coolant.
[0082] The division of the second flow channel into forward flow
section and return flow section thus does not have to be congruent
with the division of the first flow channel into the condensation
region 81 and the supercooling region 82.
[0083] The refrigerant is fed to the condenser 60 via a first fluid
supply line 63 in the upper region. The refrigerant then flows
along the first flow path 80 along the flow path 69 into the lower
region of the condenser 60. There it undergoes a diversion as a
result of an appropriate connection of the internal plate elements,
and then flows through the flow path 79 along the flow path 71 back
into the upper region of the refrigerant. Both the flow path 80 and
the flow path 79 are assigned to the condensation region 81, From
the upper region of the flow path 79, the refrigerant flows via a
first fluid discharge line 64 into the upper region of the receiver
61.
[0084] After the receiver 61 has been flowed through, the fully
condensed refrigerant flows via a second fluid supply line 65 into
the lower region of the condenser 60, which is assigned to the
supercooling region 82. The refrigerant then flows in the flow path
77 along the flow path 72 back into the upper region of the
condenser, where it is finally discharged from the condenser 60 via
the second fluid discharge line 66.
[0085] The effect of the described guidance of the coolant and the
described guidance of the refrigerant is that the coolant and the
refrigerant flow in countercurrent flow throughout the condenser
60.
[0086] The transfer of the refrigerant from the condensation region
81 to the receiver 61 takes place through the supercooling region
82 of the condenser 60. This is realized by an appropriate layout
of the individual plate elements.
[0087] The condenser 50 shown in FIG. 5 has two flow paths 79, 80
in the condensation region 81 of the first flow channel. The
supercooling region 82 has only one flow path. In differing
embodiments, also differing numbers of the flow paths can be
provided. In order to maintain the same flow-through principle as
in FIG. 5, it is advantageous if the number of flow paths in the
condensation region is even and the number of flow paths in the
supercooling region is odd.
[0088] In general, the line regions, shown here in FIGS. 3 to 5,
between the heat exchanger block and the receiver are respectively
realized by pipelines fastened to the outside of the condenser, but
also by a suitable interconnection of the internal plate elements
and an arrangement of the receiver directly on one of the outer
faces of the heat exchanger block.
[0089] The individual connecting lines between heat exchanger block
and receiver can either be jointly soldered directly with the heat
exchanger block, or realized subsequently by internal or external
pipes. Similarly, it can be provided to perform the feed or
discharge between heat exchanger block and receiver through an
appropriate design of the two outer plate elements. For instance,
it can be provided that channels are integrated into the two outer
or into just one of the outer plate elements, which channels can be
used as a supply line or discharge line.
[0090] FIG. 6 shows a schematic sectional view of the condenser. In
particular, the individual plate elements, between which are formed
the channels belonging to the first flow channel or to the second
flow channel, can be seen.
[0091] The first flow channel is flowed through by a refrigerant.
The channels belonging to the first flow channel are hatched and
marked with the reference symbol 93. The channels belonging to the
second flow channel are flowed through by a coolant and marked with
the reference symbol 94.
[0092] In addition, in FIG. 6 is represented the thermal separation
layer 92, which is disposed between the condensation region 90 and
the supercooling region 91 of the condenser. As a result of the
thermal separation layer 92, an unwanted heat transfer between the
fluids in the supercooling region 91 and the condensation region 90
is prevented.
[0093] The thermal separation layer can here be formed, for
instance, by an air-filled channel between two plate elements, by
an air gap between two adjacent plate elements, or by an
arrangement of a plurality of coolant channels side by side. Said
possibilities for the formation of a thermal separation layer are
exemplary and are by no means limiting in nature. In particularly
advantageous embodiments, in particular the heat transfer to the
refrigerant, i.e. a warming of the refrigerant, is avoided.
* * * * *