U.S. patent application number 15/580214 was filed with the patent office on 2018-06-07 for two phase distributor evaporator.
The applicant listed for this patent is Carrier Corporation. Invention is credited to Abbas A. Alahyari, Thomas D. Radcliff, Richard Rusich.
Application Number | 20180156544 15/580214 |
Document ID | / |
Family ID | 56418605 |
Filed Date | 2018-06-07 |
United States Patent
Application |
20180156544 |
Kind Code |
A1 |
Alahyari; Abbas A. ; et
al. |
June 7, 2018 |
TWO PHASE DISTRIBUTOR EVAPORATOR
Abstract
A heat exchanger is provided including a plurality of parallel
stacked plates defining at least one flow passage there between. A
manifold having a generally hollow interior is arranged adjacent
the plurality of parallel plates. An opening is disposed between
adjacent stacked plates. The opening is configured to fluidly
couple the hollow interior of the manifold and the at least one
flow passage. A distributor assembly including an insert is
disposed at least partially within the hollow interior of the
manifold. The insert includes a plurality of circumferentially
spaced axial flow channels and a plurality of radial connecting
channels arranged in fluid communication with the axial flow
channels. The radial flow channels are fluidly coupled to the at
least one flow passage via the opening.
Inventors: |
Alahyari; Abbas A.;
(Manchester, CT) ; Rusich; Richard; (Ellington,
CT) ; Radcliff; Thomas D.; (Vernon, CT) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Carrier Corporation |
Farmington |
CT |
US |
|
|
Family ID: |
56418605 |
Appl. No.: |
15/580214 |
Filed: |
June 28, 2016 |
PCT Filed: |
June 28, 2016 |
PCT NO: |
PCT/US2016/039850 |
371 Date: |
December 6, 2017 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
62186087 |
Jun 29, 2015 |
|
|
|
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F28F 3/025 20130101;
F28F 9/0278 20130101; F28D 9/005 20130101; F28D 9/0093 20130101;
F28F 2275/04 20130101; F28F 9/0275 20130101; F28F 9/027
20130101 |
International
Class: |
F28D 9/00 20060101
F28D009/00; F28F 3/02 20060101 F28F003/02 |
Claims
1. A heat exchanger, comprising: a plurality of parallel stacked
plates defining at least one flow passage there between; a manifold
arranged adjacent the plurality of parallel plates, the manifold
having a generally hollow interior; an opening disposed between
adjacent stacked plates, the opening being configured to fluidly
couple the hollow interior of the manifold and the at least one
flow passage; and a distributor assembly including an insert
disposed at least partially within the hollow interior of the
manifold, the insert including a plurality of circumferentially
spaced axial flow channels and a plurality of radial connecting
channels arranged in fluid communication with the axial flow
channels, the radial flow channels being fluidly coupled to the at
least one flow passage via the opening.
2. The heat exchanger according to claim 1, wherein a portion of
the manifold is received within at least one of the plurality of
plates.
3. The heat exchanger according to claim 1, wherein the entire
manifold is received within the plurality of plates.
4. The heat exchanger according to claim 1, wherein an edge of the
manifold is arranged in contact with an outer edge of the plurality
of plates.
5. The heat exchanger according to claim 1, further comprising a
plurality of axially spaced circumferential connecting channels
fluidly coupling the radial connecting channels to the at least one
flow passage via the opening.
6. The heat exchanger according to claim 1, wherein each of the at
least one flow passages is arranged in fluid communication with the
hollow interior of the manifold via exactly one opening.
7. The heat exchanger according to claim 1, wherein the opening is
defined by at least one of a ridge extending from at least one of
the plurality of stacked plates defining the flow passage and a
seal surrounding a portion of the manifold adjacent the flow
passage fluidly coupled thereto.
8. The heat exchanger of claim 1, comprising a seal completely
surrounding the manifold adjacent the flow passage fluidly coupled
thereto, and wherein the seal comprises an aperture defining the
opening.
9. The heat exchanger according to claim 1, wherein a fluid within
the distributor assembly is supplied to the plurality of axial flow
channels substantially equally.
10. The heat exchanger according to claim 1, wherein the
distributor assembly is configured to supply a fluid to each
opening at a substantially identical azimuthal angle.
11. The heat exchanger according to claim 1, wherein the
distributor assembly is configured to supply a fluid to each
opening at a different azimuthal angle.
12. The heat exchanger according to claim 1, wherein the
distributor assembly further comprises a nozzle arranged upstream
from the plurality of axial flow channels, the nozzle being
configured to create a homogeneous distribution of a fluid.
13. The distributor according to claim 11, wherein the nozzle
includes a constriction configured to produce a pressure drop in
the fluid.
Description
BACKGROUND
[0001] This disclosure relates generally to heat exchangers and,
more particularly, to a heat exchanger distributor assembly and a
method of distributing fluid to a heat exchanger.
[0002] Uniform distribution of two-phase fluid flow (liquid and
gas) inside heat exchangers is difficult to achieve. In heat
exchangers, such as mini-channel, microchannel, plate-fin, and
brazed-plate heat exchangers for example, distribution is
particularly difficult due to the requirement that the flow be
distributed among many layers and small ports. To overcome these
challenges, these types of heat exchangers may employ a distributor
having a closed-end tube with a series of holes in the side.
However, such distributors may not prevent separation of the
two-phase fluid under different operating conditions.
SUMMARY
[0003] According to a first embodiment, a heat exchanger is
provided including a plurality of parallel stacked plates defining
at least one flow passage there between. A manifold having a
generally hollow interior is arranged adjacent the plurality of
parallel plates. An opening is disposed between adjacent stacked
plates. The opening is configured to fluidly couple the hollow
interior of the manifold and the at least one flow passage. A
distributor assembly including an insert is disposed at least
partially within the hollow interior of the manifold. The insert
includes a plurality of circumferentially spaced axial flow
channels and a plurality of radial connecting channels arranged in
fluid communication with the axial flow channels. The radial flow
channels are fluidly coupled to the at least one flow passage via
the opening.
[0004] In addition to one or more of the features described above,
or as an alternative, in further embodiments a portion of the
manifold is received within at least one of the plurality of
plates.
[0005] In addition to one or more of the features described above,
or as an alternative, in further embodiments the entire manifold is
received within the plurality of plates.
[0006] In addition to one or more of the features described above,
or as an alternative, in further embodiments an edge of the
manifold is arranged in contact with an outer edge of the plurality
of plates.
[0007] In addition to one or more of the features described above,
or as an alternative, in further embodiments including plurality of
axially spaced circumferential connecting channels fluidly coupling
the radial connecting channels to the at least one flow passage via
the opening.
[0008] In addition to one or more of the features described above,
or as an alternative, in further embodiments each of the at least
one flow passages is arranged in fluid communication with the
hollow interior of the manifold via exactly one opening.
[0009] In addition to one or more of the features described above,
or as an alternative, in further embodiments the opening is defined
by at least one of a ridge extending from at least one of the
plurality of stacked plates defining the flow passage and a seal
surrounding a portion of the manifold adjacent the flow passage
fluidly coupled thereto.
[0010] In addition to one or more of the features described above,
or as an alternative, in further embodiments including a seal
completely surrounding the manifold adjacent the flow passage
fluidly coupled thereto. The seal comprises an aperture defining
the opening.
[0011] In addition to one or more of the features described above,
or as an alternative, in further embodiments a fluid within the
distributor assembly is supplied to the plurality of axial flow
channels substantially equally.
[0012] In addition to one or more of the features described above,
or as an alternative, in further embodiments the distributor
assembly is configured to supply a fluid to each opening at a
substantially identical azimuthal angle.
[0013] In addition to one or more of the features described above,
or as an alternative, in further embodiments the distributor
assembly is configured to supply a fluid to each opening at a
different azimuthal angle.
[0014] In addition to one or more of the features described above,
or as an alternative, in further embodiments the distributor
assembly further comprises a nozzle arranged upstream from the
plurality of axial flow channels, the nozzle being configured to
create a homogeneous distribution of a fluid.
[0015] In addition to one or more of the features described above,
or as an alternative, in further embodiments the nozzle includes a
constriction configured to produce a pressure drop in the
fluid.
BRIEF DESCRIPTION OF THE DRAWINGS
[0016] The subject matter, which is regarded as the present
disclosure, is particularly pointed out and distinctly claimed in
the claims at the conclusion of the specification. The foregoing
and other features, and advantages of the present disclosure are
apparent from the following detailed description taken in
conjunction with the accompanying drawings in which:
[0017] FIG. 1 is an example of a conventional vapor compression
system;
[0018] FIG. 2 is a exploded view of an example of a parallel flow
brazed plate heat exchanger;
[0019] FIGS. 2a-2c are cross-sectional views of various manifold
configurations;
[0020] FIG. 3 is a cross-sectional view of a portion of the
parallel flow heat exchanger of FIG. 2;
[0021] FIG. 4 is a perspective view of a distributor configured for
use in a manifold of a heat exchanger according to an embodiment of
the present disclosure;
[0022] FIG. 5 is a cross-sectional view of the distributor of FIG.
4 according to an embodiment of the present disclosure; and
[0023] FIG. 6 is a front view of a plate of a plate-fin heat
exchanger and an adjacent distribution channel fluidly coupled
thereto according to another embodiment of the present
disclosure.
[0024] The detailed description explains embodiments of the present
disclosure, together with advantages and features, by way of
example with reference to the drawings.
DETAILED DESCRIPTION
[0025] Obstacles exist to the use of microchannel heat exchangers
within a refrigerant system. In particular, refrigerant flow
maldistribution may occur in the heat exchanger when a homogeneous
two-phase mixture is allowed to phase separate in the manifold. For
example, a vapor phase of the two-phase mixture has significantly
different properties and is subjected to different effects of
internal forces than a liquid phase. This can contribute to phase
separation if the velocity of the homogeneous two-phase mixture is
reduced (e.g., as the flow area expands entering the manifold). As
a result, the flow may stratify due to deceleration in the manifold
such that the flow to each passage of the heat exchanger may not be
properly apportioned.
[0026] An example of a basic refrigerant system 20 is illustrated
in FIG. 1 and includes a compressor 22, condenser 24, expansion
device 26, and evaporator 28. The compressor 22 compresses a fluid,
such as refrigerant for example, and delivers it downstream into a
condenser 24. From the condenser 24, the refrigerant passes through
the expansion device 26 into an inlet refrigerant pipe 30 leading
to the evaporator 28. From the evaporator 28, the refrigerant is
returned to the compressor 22 to complete the closed-loop
refrigerant circuit.
[0027] Referring now to FIG. 2, an example of a heat exchanger 40,
for example configured for use as the evaporator 28 of the system
20, is illustrated in more detail. Although described with respect
to vapor compression system 20, the heat exchanger 40 of the
present disclosure may be configured for use in a plurality of
other processes, such as pumped refrigerant loops, Rankin cycles,
or other industrial heat exchange applications. In the illustrated,
non-limiting embodiment, the heat exchanger 40 is a brazed plate
heat exchanger; however, other types of heat exchangers, such as
microchannel heat exchangers and plate fin heat exchangers for
example, are within the scope of the present disclosure.
[0028] As depicted, the heat exchanger 40 comprises a plurality of
corrugated plates 42a, 42b disposed along substantially parallel
plates and being stacked in an alternating arrangement. The plates
42a, 42b may be made of stainless steel, sheet metal clad, or are
otherwise coated with a thin layer of braze material (not shown)
that provides a joining interface at contact points between
adjacent plates 42a, 42b. For assembly, plates 42a, 42b are
temporarily clamped together and heated to permanently braze plates
42a, 42b together to create alternating layers of a plurality of
primary passages 44 and a plurality of secondary passages 46
between adjacent plates 42a, 42b. The brazing operation
hermetically seals an outer peripheral edge of the plates 42a,
42b.
[0029] The actual design of the plates 42a, 42b may vary to provide
an infinite number of configurations with any number of passes and
flow patterns, such as including ridges for example. The patterns
may be formed such as by stamping, etching, engraving, extruding,
molding and embossing for example. As illustrated in FIG. 2, the
heat exchanger 40 is shown having a first fluid inlet manifold 48,
a first fluid outlet manifold 50, a second fluid inlet manifold 52,
and a second fluid outlet manifold 54. Each plate 42a, 42b includes
a first fluid supply opening 48a, 48b, a first fluid return opening
50a, 50b a second fluid supply opening 52a, 52b and a second fluid
return opening 54a, 54b, respectively. A seal (not shown) may
surround a portion of the manifold 48, 50, 52, and 54 adjacent a
flow passage to form the openings 48a, 48b, 50a, 50b, 52a, 52b,
54a, 54b.
[0030] Although the plurality of manifolds 48, 50, 52, and 54
illustrated in FIG. 2 are shown as being substantially encased by a
portion of the plates 42a, 42b, other configurations where only a
portion of one or more of the manifolds 48, 50, 52, and 54 is
received within plates 42a, 42b (FIG. 2a) or where the manifolds
48, 50, 52, and 54 are separate from but arranged in a fluid
communication with an edge of the plates 42a, 42b are within the
scope of the disclosure FIG. 2b). In one embodiment, a portion of
one of the manifolds 48, 50, 52, and 54 may be arranged in contact
with an inner edge of one of the plurality of plates 42, and
arranged in contact with an outer edge of another of the plurality
of plates 42. In the illustrated, non-limiting embodiment, the
manifolds 48, 50, 52, and 54, comprise longitudinally elongated,
generally hollow, closed end cylinders having a circular
cross-section. However, manifolds having other configurations, such
as a semi-circular, semi-elliptical, square, rectangular, or other
cross-section for example, are within the scope of the present
disclosure. The manifolds can extend from opposite end plates of
the heat exchanger 40.
[0031] When the heat exchanger 40 is used as an evaporator in an
HVAC system, such as system 20 for example, a relatively cool
refrigerant enters the heat exchanger 40 through the first fluid
supply openings 48a, 48b. Openings 48a, deliver the refrigerant to
passages 44, which convey refrigerant in a zig-zag or other
configuration between adjacent plates 42a, 42b to refrigerant
return openings 50a, 50b. Openings 50a and 50b then direct the
refrigerant to outlet manifold 50 to recycle the refrigerant
through the system. Similarly, a second fluid to be cooled enters
the heat exchanger 40 through inlet manifold 52 and flows through
the openings 52a, 52b. Openings 52b of the heat exchanger 40
deliver the second fluid to passages 46, which convey the second
fluid in a zig-zag or other configuration between adjacent plates
42a, 42b to the second fluid return openings 54a, 54b. As the
second fluid flows through passages 46, the refrigerant in the
adjacent passages 44 cools the second fluid. After the second fluid
is cooled, openings 54a, 54b direct the chilled second fluid to the
second fluid outlet manifold 54, where it is then provided to an
environment to be conditioned.
[0032] Referring now to FIGS. 3-6 a longitudinally elongated
distributor assembly 70 configured for use within the interior
volume of an inlet manifold, such as refrigerant inlet manifold 48
of heat exchanger 40, is illustrated. Although illustrated within a
horizontally arranged manifold 48, the distributor assembly 70 may
also be used in any or non-horizontal orientation (e.g., a vertical
orientation). The distributor assembly 70 extends over at least a
portion, if not the entire length of the inlet manifold 52. In
addition, the distributor assembly 70 may be centered within the
manifold 48, or alternatively, may be off-center, such as skewed
towards a wall of the manifold 48 opposite the plates 42a, 42b for
example.
[0033] The distributor assembly 70 includes an insert 72 having a
cross-sectional shape including, but not limited to, round,
elliptical, and rectangular for example. In one embodiment, the
size and shape of the insert 72 is generally complementary to the
manifold 48. The insert 72 has a plurality of distribution flow
paths 74 formed therein such that the refrigerant provided at an
inlet of the manifold 52, such as from line 30 of the vapor
refrigerant circuit 20 for example, is distributed substantially
equally between the flow paths 74. The refrigerant flow paths 74
extend from an internal cavity of the distributor insert 72 to the
flow passage 44 formed between adjacent heat exchanger plates 42a,
42b. The distribution flow paths 74 are sized to maintain the
velocity of the two-phase mixture (e.g., so as to limit phase
separation) and may be any shape such as round, rectangular, oval,
or any other shape for example. In addition, the distribution flow
paths 74 may take any path, such as a helical path, or a linear
path with a metered bend for example.
[0034] By separating a two-phase mixture with a known liquid-vapor
distribution (e.g., a homogeneous distribution, where no
significant portions of the flow volume contain only one phase)
into the plurality of distribution flow paths 74, the likelihood
that the distribution of the two-phase mixture settles or
redistributes (except within each flow paths 74) can be reduced. In
addition, if each of the plurality of distribution flow paths 74 is
formed having an appropriately small diameter, for example between
about 0.2 mm and 5 mm, redistribution of the phases of the flow is
unlikely to occur because the slip between the velocity of the
liquid portion and the vapor portion of the refrigerant is
minimized. In an embodiment, the plurality of distribution flow
paths 74 have equal diameters (excepting for normal manufacturing
variation in dies or other manufacturing tools due to imprecision
in the tool construction or wear). In another embodiment, the
diameter of each flow paths 74 is selected to reduce the variation
in flow resistance between different flow circuits of the heat
exchanger (to nearly match pressure drop characteristics of each
flow path between the manifold inlet to the manifold outlet of the
heat exchanger).
[0035] In the illustrated, non-limiting embodiment, each of the
plurality of distribution flow paths 74 includes a first portion or
flow channel 76 extending axially over at least a portion of the
length of the insert 72. The axial flow channels 76 may be parallel
to and circumferentially spaced about a central axis of the insert
72, such as in an equidistantly spaced configuration for example.
As shown in FIG. 3, the plurality of axial flow channels 76 may
vary in length to provide a fluid flow to one or more corresponding
passages 44 via refrigerant supply openings 48a, 48b. Variation in
the lengths of the axial flow channels 76 may additionally be used
to equalize the pressure drop of the fluid, and therefore the flow
between the plurality of axial flow channels 76. Alternatively, the
plurality of axial flow passages 76 may be substantially identical
in length, such as extending over the full length of the insert 72,
as shown in FIG. 5 for example.
[0036] The distribution flow paths 74 additionally include a
plurality of axially spaced connecting channels 78, each of which
is configured to fluidly couple at least one of the axial flow
channels 76 to a refrigerant supply opening 48a, 48b and one or
more of the passages 44 formed between adjacent plates 42a, 42b.
Accordingly, at least one connecting channel 78 is arranged in
fluid communication with each of the plurality of axial flow
channels 76. As shown in FIG. 3, each of the plurality of
connecting channels 78 extends radially outward from an axial flow
channel 76 to a distribution hole 80 formed in an outer surface 82
of the insert 72. In such embodiments, the connecting channels 78
are at least partially integrally formed with the insert 72.
[0037] One or more of the plurality of connecting channels 78 may
additionally extend at least partially around a circumference of
the insert 72. In one embodiment, the circumferential portion of
the plurality of connecting channels 78 may be integrally formed as
a portion of the heat exchanger plates 42a, 42b (FIG. 6). In
another embodiment, the circumferential portion of the plurality of
connecting channels 78 may be formed in one or both of the exterior
surface 82 of the insert 72 and an inner surface 49 of the manifold
48. The distributor assembly 70 may additionally include an outer
sleeve 84, as shown in FIGS. 4 and 5, arranged in an overlapping
configuration with the insert 72 and being configured to define a
portion of the connecting channels 78 to retain fluid therein. A
distributor assembly 70 having circumferentially extending
connecting channels 78 and an outer sleeve 84 is described in more
detail in U.S. Patent Publication No. US2014/0345837, filed on May
23, 2013, the entire contents of which are incorporated herein by
reference.
[0038] As shown, a plurality of distribution holes 80 may be formed
in either the outer surface 82 of the insert 72 or in an outer
sleeve 84 positioned about the insert 72 and are fluidly connected
to not only the distribution flow paths 74 but also the openings
48a, 48b connected to passages 44. In another configuration, the
plurality of distribution holes 80 may be replaced by one or more
continuous slots. In embodiments having a plurality of distinct
distribution holes 80, each distribution hole 80 may be connected
to one or more corresponding connecting channels 78. Alternatively,
a plurality of distribution holes 80 may be configured to receive a
fluid flow from a single connecting channel 78.
[0039] In the illustrated, non-limiting embodiment of FIG. 4, the
distribution holes 80 are arranged along a horizontal axis such
that the position of each hole 80 about the circumference of the
housing distributor assembly 70 is substantially identical. As a
result, the refrigerant flow is delivered to each of the
refrigerant supply openings 48a, 48b at the same azimuthal angle.
In another embodiment (FIG. 3), the distribution holes 80 are
positioned at different circumferential angles relative to one
another.
[0040] Referring again to FIGS. 4 and 5, the distributor 70 may
also include a nozzle or orifice 90 arranged generally upstream
from the plurality of axial flow channels 76. The nozzle 90 may be
a separate component positioned adjacent an end of the insert 72,
or alternatively, may be located within a hollow region of the
insert 72. In such embodiments, the nozzle 90 is fluidly coupled to
line 30 of the vapor refrigerant circuit 20 (FIG. 1) such that
substantially all of the refrigerant from the expansion device 26
is configured to flow directly into the insert 72 via the nozzle
90. The nozzle 90 includes an orifice that restricts the
cross-sectional area of the fluid inlet path and is configured to
increase the velocity of the fluid flowing there through.
Increasing the velocity 14 advantageously provides a substantially
uniform, homogeneous mixture of fluid 14. In one embodiment, the
orifice of the nozzle 90 comprises a venturi portion to reduce the
pressure drop of the fluid passing there through. The homogenous
two-phase refrigerant mixture may be output from the nozzle 90 in a
generally conical shape and is supplied to the plurality of
distribution flow paths 74 formed in the insert 72 (see FIG.
5).
[0041] The distributor assembly 70 as disclosed herein is
configured to provide more uniform distribution to a plurality of
flow passages of a heat exchanger 40, particularly a heat exchanger
configured as an evaporator, and even more particularly a brazed
plate heat exchanger. This homogenized distribution will result in
improved performance over a wider range of flow conditions. As a
result, a refrigerant system 20 including the heat exchanger 40
will have an increased coefficient of performance and reduced power
consumption.
Embodiment 1
[0042] A heat exchanger is provided including a plurality of
parallel stacked plates defining at least one flow passage there
between. A manifold having a generally hollow interior is arranged
adjacent the plurality of parallel plates. An opening is disposed
between adjacent stacked plates. The opening is configured to
fluidly couple the hollow interior of the manifold and the at least
one flow passage. A distributor assembly including an insert is
disposed at least partially within the hollow interior of the
manifold. The insert includes a plurality of circumferentially
spaced axial flow channels and a plurality of radial connecting
channels arranged in fluid communication with the axial flow
channels. The radial flow channels are fluidly coupled to the at
least one flow passage via the opening.
Embodiment 2
[0043] The heat exchanger according to embodiment 1, wherein a
portion of the manifold is received within at least one of the
plurality of plates.
Embodiment 3
[0044] The heat exchanger according to either embodiment 1 or 2,
wherein the entire manifold is received within the plurality of
plates.
Embodiment 4
[0045] The heat exchanger according to either embodiment 1 or 2,
wherein an edge of the manifold is arranged in contact with an
outer edge of the plurality of plates.
Embodiment 5
[0046] The heat exchanger according to any of the preceding
embodiments, further comprising a plurality of axially spaced
circumferential connecting channels fluidly coupling the radial
connecting channels to the at least one flow passage via the
opening.
Embodiment 6
[0047] The heat exchanger according to any of the preceding
embodiments, wherein each of the at least one flow passages is
arranged in fluid communication with the hollow interior of the
manifold via exactly one opening.
Embodiment 7
[0048] The heat exchanger according to any of the preceding
embodiments, wherein the opening is defined by at least one of a
ridge extending from at least one of the plurality of stacked
plates defining the flow passage and a seal surrounding a portion
of the manifold adjacent the flow passage fluidly coupled
thereto.
Embodiment 8
[0049] The heat exchanger of any of embodiments 1-6, comprising a
seal completely surrounding the manifold adjacent the flow passage
fluidly coupled thereto, and wherein the seal comprises an aperture
defining the opening.
Embodiment 9
[0050] The heat exchanger according to any of the preceding
embodiments, wherein a fluid within the distributor assembly is
supplied to the plurality of axial flow channels substantially
equally.
Embodiment 10
[0051] The heat exchanger according to any of the preceding
embodiments, wherein the distributor assembly is configured to
supply a fluid to each opening at a substantially identical
azimuthal angle.
Embodiment 11
[0052] The heat exchanger according to any of the preceding
embodiments, wherein the distributor assembly is configured to
supply a fluid to each opening at a different azimuthal angle.
Embodiment 12
[0053] The heat exchanger according to any of the preceding
embodiments, wherein the distributor assembly further comprises a
nozzle arranged upstream from the plurality of axial flow channels,
the nozzle being configured to create a homogeneous distribution of
a fluid.
Embodiment 13
[0054] The distributor according to embodiment 11, wherein the
nozzle includes a constriction configured to produce a pressure
drop in the fluid.
[0055] While the present disclosure has been particularly shown and
described with reference to the exemplary embodiments as
illustrated in the drawing, it will be recognized by those skilled
in the art that various modifications may be made without departing
from the spirit and scope of the present disclosure. Therefore, it
is intended that the present disclosure not be limited to the
particular embodiment(s) disclosed as, but that the disclosure will
include all embodiments falling within the scope of the appended
claims.
* * * * *