U.S. patent application number 17/046304 was filed with the patent office on 2021-05-13 for heat exchanging apparatus and method of supporting tube bundle within heat exchanger.
This patent application is currently assigned to Koch Heat Transfer Company, LP. The applicant listed for this patent is Koch Heat Transfer Company, LP. Invention is credited to Nathan BARNETT, Byron BLACK, Marco FAZZINI, Prashant JADHAV, Donald WOODS.
Application Number | 20210140715 17/046304 |
Document ID | / |
Family ID | 1000005401170 |
Filed Date | 2021-05-13 |
![](/patent/app/20210140715/US20210140715A1-20210513\US20210140715A1-2021051)
United States Patent
Application |
20210140715 |
Kind Code |
A1 |
BLACK; Byron ; et
al. |
May 13, 2021 |
HEAT EXCHANGING APPARATUS AND METHOD OF SUPPORTING TUBE BUNDLE
WITHIN HEAT EXCHANGER
Abstract
A heat-exchange apparatus comprising a plurality of tubes
bundled together, each having segmented twisted segments is
disclosed. Each of the plurality of tubes provides a tube body
defining an interior passageway for carrying a first fluid and a
plurality of segments along its length comprising a straight
section and a twisted section that are in fluid communication with
each other. Each of the plurality of tubes provides a central
longitudinal axis along its length. The tube body along the twisted
section exhibits rotation about the central longitudinal axis and
the tube body along the straight section exhibits no rotation. An
exterior surface of the tube body of a tube can come into contact
with an exterior surface of the tube body of another tube along the
twisted section, whereas the exterior surfaces of such tubes avoid
contact along the straight section.
Inventors: |
BLACK; Byron; (Houston,
TX) ; JADHAV; Prashant; (Houston, TX) ;
FAZZINI; Marco; (Houston, TX) ; WOODS; Donald;
(Houston, TX) ; BARNETT; Nathan; (Houston,
TX) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Koch Heat Transfer Company, LP |
Houston |
TX |
US |
|
|
Assignee: |
Koch Heat Transfer Company,
LP
Houston
TX
|
Family ID: |
1000005401170 |
Appl. No.: |
17/046304 |
Filed: |
April 18, 2019 |
PCT Filed: |
April 18, 2019 |
PCT NO: |
PCT/IB2019/053246 |
371 Date: |
October 9, 2020 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
62660089 |
Apr 19, 2018 |
|
|
|
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F28D 7/163 20130101 |
International
Class: |
F28D 7/16 20060101
F28D007/16 |
Claims
1. A heat-exchanging apparatus comprising: a plurality of tubes
bundled adjacent one another, each of the plurality of tubes having
a tube body defining an interior passageway for carrying a first
fluid, each of the plurality of tubes having a plurality of
segments along its length comprising a straight section and a
twisted section in fluid communication with each other; wherein
each of the plurality of tubes has a central longitudinal axis
along its length, the tube body along the twisted section
exhibiting rotation about the central longitudinal axis, the tube
body along the straight section exhibiting no rotation about the
central longitudinal axis, and an exterior surface of the tube body
of a first tube of the plurality of tubes coming into contact with
an exterior surface of the tube body of a second tube of the
plurality of tubes along the twisted section, the exterior surfaces
of the first and second tubes avoiding contact along the straight
section.
2. The heat-exchanging apparatus of claim 1 further comprising an
area around and between the plurality of tubes, the area forming a
passageway for carrying a second fluid.
3. The heat-exchanging apparatus of claim 1 wherein the plurality
of segments of each tube comprises an alternating arrangement of
straight and twisted sections, wherein the twisted section is
located between first and second straight sections and the straight
section is located between first and second twisted sections.
4. The heat-exchanging apparatus of claim 3 wherein the alternating
arrangement of straight and twisted sections of each of the
plurality of tubes are in line with one another, the twisted
section of the first tube being adjacent the twisted section of the
second tube, the straight section of the first tube being adjacent
to the straight section of the second tube.
5. The heat exchanging apparatus of claim 1 wherein rotation of the
tube body of each of the plurality of tubes in the twisted section
is synchronized such that rotation of the first tube corresponds
with rotation of the second tube.
6. The heat-exchanging apparatus of claim 2 wherein rotation of the
tube body along the at least one twisted section causes the second
fluid to exhibit a swirling action as it flows along the twisted
section.
7. The heat exchanging apparatus of claim 1 wherein the tube body
of each of the plurality of tubes is rotated at least 360.degree.
about its central longitudinal axis along each of the twisted
sections, contact points between the twisted section of the first
tube and adjacent twisted sections of other adjacent tubes of the
plurality of tubes being made at rotation intervals on the order of
60.degree. through said 360.degree. rotation.
8. The heat exchanging apparatus of claim 1 wherein upon entering
the twisted section the each of the plurality of tubes are in a
first rotation orientation whereby the exterior surface of the tube
body of the first tube contacts the exterior surface of the tube
body of the second tube, the exterior surfaces of the tube bodies
of the first and second tubes separating from one another as the
tubes rotate through the twisted section away from the first
rotation orientation and coming back into contact with one another
when the tubes are rotated at rotation intervals on the order of
180.degree. from the first rotation orientation.
9. The heat exchanging apparatus of claim 8 wherein the exterior
surface of the tube body of the first tube comes into contact with
an exterior surface of a tube body of a third tube of the plurality
of tubes when the tubes are rotated at rotation intervals on the
order of 60.degree. and 240.degree. from the first rotation
orientation.
10. The heat exchanging apparatus of claim 1 wherein the tube body
of each of the plurality of tubes has a substantially round
cross-section profile occupying a given area along the straight
section, the round cross-section profile being compressed through
the twisted section, said compression causing a reduction of the
given area and flattening of the round cross-section profile
whereby opposing points of said round cross-sectional profile
protrude outward.
11. The heat exchanging apparatus of claim 10 wherein outward
protrusion of opposing points of the tube body of the first tube in
the twisted section permits contact with opposing points of the
tube body of the second tube.
12. A heat exchanger comprising: a plurality of tubes bundled
adjacent one another, each of the plurality of tubes having a tube
body defining an interior passageway for carrying a first fluid,
each of the plurality of tubes having a plurality of segments along
its length comprising a plurality of alternating straight sections
and a plurality of twisted sections in fluid communication with
each other, the straight sections of the plurality of tubes being
in alignment with one another and the twisted sections of the
plurality of tubes being in alignment with one another; a shell
surrounding the plurality of tubes, the shell defining an area
around and between the plurality of tubes, the area forming a
passageway for carrying a second fluid; wherein each of the
plurality of tubes has a central longitudinal axis along its
length, the tube body along the twisted sections exhibiting
rotation about the central longitudinal axis, the tube body along
the straight sections exhibiting no rotation about the central
longitudinal axis; an exterior surface of the tube body of a first
tube of the plurality of tubes coming into contact with an exterior
surface of the tube body of a second tube of the plurality of tubes
along the twisted sections, the exterior surfaces of the first and
second tubes avoiding contact along the straight sections.
13. The heat exchanger of claim 12 wherein rotation of the tube
body of each of the plurality of tubes in the twisted sections is
synchronized where rotation of the first tube corresponds to
rotation of the second tube.
14. The heat exchanger of claim 12 wherein rotation of the tube
body along the twisted sections causes the second fluid to exhibit
a swirling action as it flows along the twisted sections.
15. The heat exchanger of claim 12 wherein the tube body of each of
the plurality of tubes is rotated at least 360.degree. along the
twisted sections, contact between adjacent tubes being made at
rotation intervals on the order of 60.degree. through said rotation
of said tube bodies.
16. The heat exchanger of claim 12 wherein the tube body of each of
the plurality of tubes has a substantially round cross-section
profile occupying a given area along the straight sections, the
round cross-section profile being compressed through the twisted
sections, said compression causing a reduction of the given area
and flattening of the round cross-section profile whereby opposing
points on said profile protrude outward.
17. The heat exchanger of claim 16 wherein outward protrusion of
opposing points of the tube body of the first tube in the twisted
sections permits contact with opposing points of the tube body of
the second tube.
18. A method of carrying out heat exchange comprising: introducing
a first fluid into a plurality of tubes of a heat exchanging
apparatus, the plurality of tube being bundled together, the each
of the plurality of tubes having a central longitudinal axis along
its respective length and comprising a plurality of straight
sections and a plurality of twisted sections, the plurality of
straight sections and plurality of twisted sections being in an
alternating arrangement along a length of the tubes, the plurality
of twisted sections exhibiting rotation about the about the central
longitudinal axis, the plurality of straight sections exhibiting no
rotation about the central longitudinal axis; directing a second
fluid into the heat exchanging apparatus into an area adjacent the
plurality of bundled tubes; permitting the first fluid to flow
within the plurality of tubes through the alternating arrangement
of straight sections and twisted sections; supporting the plurality
of tubes within the heat exchanging apparatus at contact points
along the plurality of twisted sections, the contact points being
locations along the plurality of twisted sections where adjacent
tubes of the plurality of tubes contact one another.
19. The method of claim 16 further comprising causing the second
fluid to exhibit a swirling action as it flows along the plurality
of twisted sections.
20. (canceled)
21. The method of claim 19 wherein forming the plurality of
segments along the length of each of the plurality of tubes further
comprising rotating each tube body of each twisted section at least
360.degree. about its central longitudinal axis, said rotation of
each twisted section along a first tube of the plurality of tubes
providing contact points with adjacent twisted sections of other
adjacent tubes of the plurality of tubes at rotation intervals on
the order of 60.degree..
Description
FIELD
[0001] Embodiments of the present invention relate generally to a
heat exchanging apparatus, heat exchanger, method of use and method
of manufacturing, and more particularly to embodiments providing a
plurality of bundled round heat exchange tubes comprising
individually segmented sections generally having a twisted
configuration capable of operably self-supporting the respective
tubes within the heat exchanger.
CROSS-REFERENCE TO RELATED APPLICATIONS
[0002] The present application claims priority to and incorporates
by reference in its entirety U.S. Provisional Patent Application
No. 62/660,089 titled "Tube Bundle for Heat Exchanger and Method of
Supporting Same within Heat Exchanger Shell" filed on Apr. 19,
2018.
BACKGROUND
[0003] Tubular heat exchangers, including shell-and-tube and
hairpin (multitube) type heat exchangers, are used in a wide
variety of applications to create heat exchange between streams of
various fluids. Such heat exchangers generally include a
combination, or bundle, of tubes housed within a cylindrically
shaped shell. In operation, a first fluid, commonly referred to as
the "tube-side fluid," is directed through at least some of the
tubes of the tube bundle. Concurrently, a second fluid, commonly
referred to as the "shell-side fluid," is directed within the shell
and into any void around the tubes comprising the tube bundle,
wherein the tube wall of each tube can permit heat exchange between
the tube-side fluid stream flowing within the tubes and the
shell-side fluid stream flowing around the tubes.
[0004] Generally, the tube bundle of a tubular heat exchanger
includes a plurality of separate, self-contained individual tubes
that extend in parallel to each other, wherein one or both of the
ends of each respective tube is fixed to a header plate or a
plurality of header plates, which are known as tube sheets. In
applications that demand generally elongated heat exchangers of
various lengths, known tubes and tube bundles, and the various
designs thereof, of tubular heat exchangers, including
shell-and-tube or hairpin (multitube) type heat exchangers, are
subject to sagging and vibrations, both of which can negatively
affect the heat exchanger and its components. To mitigate the
negative effects of tube sagging and vibration, known tubes and
tube bundles of tubular heat exchangers require intermediate
support structures or members at various points over the length of
the tubes or tube bundle. Such intermediate support structures or
members can include spaced-apart baffles (e.g., segmented baffles),
which generally consist of plates having holes or openings to
receive and support the tubes and may further include spaces or
voids for permitting the flow of shell-side fluid. In addition to
supporting the tubes and maintaining the desired position of the
same within the shell, such baffles may generally redirect the flow
of the shell-side fluid, such that it flows across, rather than
along, the tubes. In this way, such baffles generally inhibit the
flow of the shell-side fluid along the length of the tubes. Other
types of supports can consist of grids or rods.
[0005] Although baffles designs can vary and have any number of
configurations and features to suit a particular application,
baffle positioning and spacing can pose a difficult design
challenge and create an impediment to efficient and optimal heat
exchanger operation. In particular, when the spacing between a
series of baffles is reduced to address the sagging and vibration
of a specific tube or tube bundle, the limited space between the
baffles can adversely affect the heat exchanger by reducing the
flow area for the shell-side fluid, which results in excessive
shell-side pressure drop.
[0006] Thus, there is a need in the art for an improved design for
a tube, a tube bundle, and a heat exchanger that can effectively
support the tube or the tube bundle within the shell for use in
connection with low shell-side pressure drop designs or
applications, while also avoiding sagging and vibration of the
tubes.
FIGURES
[0007] FIG. 1 is a perspective view of an exemplary heat exchanger
in accordance with embodiments presented herein;
[0008] FIG. 2 is a partial side elevation schematic representation
of an exemplary heat exchanger in accordance with embodiments
presented herein;
[0009] FIG. 3 is a partial detail side representation of tube
sections of a heat exchanger in accordance with embodiments
presented herein;
[0010] FIG. 4 is a cross-sectional representation taken generally
along line 4-4 of FIG. 3 in the direction of the arrows and showing
a tube bundle in accordance with the embodiment shown in FIG.
3;
[0011] FIG. 5 is a cross-sectional representation taken generally
along line 5-5 of FIG. 3 in the direction of the arrows and showing
a tube bundle in accordance with the embodiment shown in FIG.
3;
[0012] FIG. 6 is a cross-sectional representation taken generally
along line 6-6 of FIG. 3 in the direction of the arrows and showing
a tube bundle in accordance with the embodiment shown in FIG.
3;
[0013] FIG. 7 is a cross-sectional representation taken generally
along line 7-7 of FIG. 3 in the direction of the arrows and showing
a tube bundle in accordance with the embodiment shown in FIG.
3;
[0014] FIG. 8 is a cross-sectional representation taken generally
along line 8-8 of FIG. 3 in the direction of the arrows and showing
a tube bundle in accordance with the embodiment shown in FIG.
3;
[0015] FIG. 9 is a cross-sectional representation taken generally
along line 9-9 of FIG. 3 in the direction of the arrows and showing
a tube bundle in accordance with the embodiment shown in FIG. 3;
and
[0016] FIG. 10 is a cross-sectional representation taken generally
along line 10-10 of FIG. 3 in the direction of the arrows and
showing a tube bundle in accordance with the embodiment shown in
FIG. 3.
DETAILED DESCRIPTION
[0017] Embodiments presented herein are generally directed to a
heat-exchanging apparatus, a heat exchanger, a method of
manufacture and method of carrying out heat exchange providing
segmented twisted sections of bundled heat exchange tubes.
Embodiments disclosed herein can be provided or practiced with any
number of exemplary heat exchanger designs, including for example a
shell-and-tube or hairpin (multitube) type heat exchanger or
multi-pass arrangements, and/or designs implementing parallel
(co-current) or counter-flow arrangements.
[0018] With reference to the drawings, FIG. 1 schematically depicts
a perspective illustration of a heat exchanger 100 according to an
exemplary embodiment of the present invention. As best illustrated
in FIG. 1, a tubular heat exchanger 100 can be generally elongated
and comprise an inlet 102, an outlet 104, and tubes 120 or a tube
bundle 140. The tubular heat exchanger 100 of FIG. 1 is depicted
without a shell or other common heat exchanger components (e.g., a
shroud, and so on). However, it will be understood that heat
exchanger 100 may comprise such components without limitation.
[0019] FIG. 2 representatively illustrates a partial side schematic
representation view of a heat exchanger 100 according to an
exemplary embodiment provided herein, and more particularly to an
exemplary bundle 140 of individual tubes 120 having a generally
U-shaped arrangement. As shown in FIG. 2, the U-shaped bundle 140
of tubes 120 can comprise a plurality of generally elongated tubes
120 having at least a first leg portion 142 and a second leg
portion 144 extending substantially parallel to each other along
their lengths. According to the embodiment illustrated in FIG. 2,
it will be recognized that portions 142, 144 of tubes 120 within
the tube bundle 140 are in fluid communication with each other so
that tube-side fluid within an interior passageway of the tubes can
be permitted to flow in a first direction along the first leg
portion 142 of a U-shaped tube 120 from an inlet 102 and into the
U-shaped portion 146, where the tube-side fluid can reverse
direction and flow back in a second direction, opposite to the
first direction, along the second leg portion 144 of a U-shaped
tube 120 to an outlet 104.
[0020] Although FIG. 2 depicts the tube bundle 140 generally
comprising a linear first leg portion 142 and a linear second leg
portion 144 that are joined by a generally U-shaped portion 146, it
will be understood that the tube bundle 140 can comprise any of a
number of shapes, whether presently known or later developed,
including, without limitation, generally triangular shapes,
generally rectangular shapes, and any similar symmetrical and
non-symmetrical shapes or series of shapes that are joined by any
number of rounded portions that have varying arc lengths and radius
sizes. Further, a preferred embodiment of the present invention can
be used with alternate tube bundle arrangements including, for
example, straight tube or shell arrangements, single or multi-pass
arrangements, and/or designs implementing parallel (co-current) or
counter-flow arrangements.
[0021] As shown schematically in FIG. 2, according to exemplary
embodiments the fluid tubes 120 of the tube bundle 140 can
generally comprise an alternating series of individually segmented
sections 150, in fluid communication with each other, comprising
generally tubular straight sections 152 and sections further
generally comprising a twisted configuration 154, which are twisted
or rotated along their lengths about the respective central
longitudinal axes 160 defined thereby. For example, FIG. 2
illustrates the first leg portion 142 and the second leg portion
144 of each tube 120 as having four straight sections 152 and three
twisted sections 154 along their lengths, including (in sequence,
from left to right): a first straight section 152, a first twisted
section 154, a second straight section 152, a second twisted
section 154, a third straight section 152, a third twisted section
154, and a fourth straight section 152 leading into the U-shaped
portion 146. Thus, each tube 120 of the tube bundle 140 is shown as
providing a series 150 of intermittent twisted sections 154 spaced
apart by straight or untwisted tube sections 152. However, it will
be understood that a preferred embodiment of the present invention
can comprise a first straight section 152, generally corresponding
with the entire length of the first leg portion 142, and a first
twisted section 154, generally corresponding with the entire length
of the second leg portion 144, or any variation thereof. Further,
although FIG. 2 depicts the alternating series of individually
segmented sections 150 as being generally equal or consistent in
length, it will be understood that the length of any straight
section 152 or any twisted section 154 can vary relative to any
other straight section 152 or twisted section 154. According to
exemplary embodiments as shown schematically in FIG. 2, the twisted
tube sections 154 of the plurality of tubes can be generally
positioned in alignment with one another and the straight tube
sections 152 can be generally positioned in alignment with one
another.
[0022] As shown schematically in FIG. 2, in a preferred embodiment,
the intermittent twisted sections 154 of the first leg portion 142
and the intermittent twisted sections 154 of the second leg portion
144 of each tube 120 within the tube bundle 140 can be aligned so
that the twisted sections 154 of each leg portion are generally
laterally adjacent to the twisted sections 154 of the other leg
portion. Although FIG. 2 illustrates a specific number and location
of alternating twisted sections 154 and straight sections 152, it
will be understood that embodiments are not limited to such and
that such alternating sections 150 can be provided in alternative
numbers or locations, without limitation.
[0023] The twisted sections 154, interspersed between straight
sections 152, are advantageous because they can generally result in
a more efficient conversion of pressure drop across the shell-side
of the tubes 120 and the tube bundle 140. Specifically, the twisted
sections 154, and the arrangement thereof, can mitigate the
negative effects of tube sagging and vibration of the tubes 120,
because the twisted sections 154, and the arrangement thereof,
increases the mechanical resonant frequency of the tube 120, which
can make the tubes 120 and any bundle 140 of such tubes 120 more
resistant to lateral deflection from forces generated by shell-side
fluid flow through the heat exchanger 100. In this way, the twisted
sections 154, and the arrangement thereof with straight sections
152, eliminate the need for closely-spaced intermediate support
structures or members at various points along the length thereof
and, in some instances, the need for intermediate support
structures or members at all. The improvement being advantageous
over tubes, arrangements of tubes, and tube bundles that comprise
either entirely straight tubes or tubes that are twisted over their
entire lengths, without the alternating series of individually
segmented straight sections and twisted sections 150. Further, the
twisted sections 154 can promote the efficiency of heat transfer
between tube-side fluid and shell-side fluid when compared to known
tube arrangements. First, by eliminating the need for
closely-spaced intermediate support structures or members at
various points on the length of the tube 120 or tube bundle 140,
such configuration requires less baffles, or even no baffles, to
support and maintain the tubes 120 or the tube bundle 140, which
reduces the inhibiting effect of such baffles on the flow of the
shell-side fluid along the length of the tubes. Second, by
eliminating the need for closely-spaced intermediate support
structures or members at various points on the length of the tube
120 or tube bundle 140, such configuration does not create the
excessive shell-side pressure drop common to known configurations
and spacings of baffles used in heat exchangers.
[0024] FIG. 3 representatively illustrates a partial detail
representation of the side of a twisted section 154 of three (3)
tubes 120 of a tube bundle 140 according to exemplary embodiment.
FIGS. 4-10 further depict representations of the various
cross-sections at specific rotational intervals along the length of
a segment S of the respective tubes 120 in FIG. 3. As best shown in
FIGS. 3-10, between segment S, each tube 120 is twisted or rotated
about a central longitudinal axis 160 at least 360.degree., or one
complete revolution, with each cross-section view along segment S
showing rotation on the order of approximately 60.degree. from any
immediately adjacent cross-section. In a preferred embodiment, the
segment S can be approximately between three (3) inches and sixteen
(16) inches, or approximately between five (5) inches and ten (10)
inches, depending on the diameter of the respective tube 120, which
can vary between approximately 0.625 inches in diameter and one (1)
inch in diameter. In a preferred embodiment, each tube 120 can
complete two 360.degree. turns between any two consecutive straight
sections 152. As shown schematically in FIG. 3, the exterior
surfaces of tubes 120 avoid contact along the straight sections
152.
[0025] FIGS. 4-10 schematically illustrate rotation of tubes 120
within a tube bundle 140 through a 360.degree. portion of rotation
along the twisted section 154. Although the tubes 120 according to
exemplary embodiments presented herein are generally provided as
having a round cross-section profile when oriented along the
straight sections, FIGS. 4-10 show that such round cross-sectional
profile is compressed through the twisting of the tube bodies.
According to exemplary embodiments, such compression can flatten
the round-cross sectional profile such that the tubes take on a
generally elliptical shape as shown in FIGS. 4-10. Such compression
can reduce the cross-sectional area of the tubes and causes
opposing points on the sides of the tubes to protrude outward. As
shown schematically in FIGS. 4-10, such protrusion can bring about
contact 170 between exterior surfaces of tube bodies of adjacent
tubes.
[0026] As shown schematically in FIGS. 4-10, exterior surfaces of
adjacent tubes 120 of the tube bundle 140 can have a plurality of
points of contact 170 along the twisted section at certain rotation
intervals. According to exemplary embodiments shown in FIGS. 4-10,
rotation of the tube body of each of the plurality of tubes 120 in
the twisted section can be synchronized such that the tubes 120
rotate together. For example, at commencement of a twisted section
as shown representatively in FIG. 4, the plurality of tubes 12 can
be in an initial rotation orientation. From this orientation, as
the tubes twist along the twisted segment, the tube body of each
tube rotate together (tubes shown as being horizontally adjacent to
one another in FIG. 4 with their end points in contact are shown as
rotating counterclockwise towards the rotation interval shown in
FIG. 5). In undergoing such rotation, the tubes shown as being in
contact with one another in FIG. 4 taper away from one another and
form new contacts (with another tube) at the rotation interval of
FIG. 5. Such contact and separation continues as the tubes rotate
through the twisted section. It will be recognized that FIG. 7
represents a rotation interval taken on the order of 180.degree.
from the initial rotation orientation of FIG. 4. Accordingly, the
right side of a tube in FIG. 4 would be shown as being the left
side in FIG. 7.
[0027] Each of FIGS. 4-10 show tubes 120 of an exemplary tube
bundle 140 at a particular rotation interval taken on the order of
60.degree. through a full 360.degree. of rotation of a twisted
segment. For example, with respect to an interior tube of the tube
bundle 140 in FIG. 4 which is surrounded by adjacent perimeter
tubes, such interior tube 120 can have a first point of contact 170
with an adjacent tube 120 directly to its right and a second point
of contact 170 with the adjacent tube 120 directly to its left. In
FIG. 5, the centermost tube has the first point of contact 170 with
the adjacent tube 120 to its upper-right and the second point of
contact 170 with the adjacent tube 120 to its lower-left. In FIG.
6, the centermost tube 120 has the first point of contact 170 with
the adjacent tube 120 to its upper-left and the second point of
contact 170 with the adjacent tube 120 to its lower-right. Then, in
FIG. 7, the centermost tube 120 has the first point of contact 170
with the adjacent tube 120 directly to its left and the second
point of contact 170 with the adjacent tube 120 directly to its
right. In this way, the centermost tube 120 can encounter eight (8)
different points of contact 170 through 180.degree. of revolution
along a portion of segment S, as represented by FIGS. 4-7. In
contrast, as shown in FIGS. 4-7, with respect to any tube 120 other
than the centermost tube 120 in tube bundle 140, such tube can
encounter four (4) different points of contact 170 through
180.degree. of revolution along a portion of segment S. Although
FIGS. 4-10 depict twisted section 154 of a tube bundle 140
comprising seven individual tubes 120, with various points of
contact 170, it will be understood that the tube bundle 140 can
comprise any number of tubes 120 with any number of points of
contacts 170 without limitation.
[0028] According to embodiments presented herein, and shown
representatively in FIGS. 2-10, the intermittent twisted sections
154 of the tubes 120 can act as a support mechanism within the heat
exchanger shell and further eliminate the need for baffles
altogether. Further, the twisted nature of the twisted sections 154
permits for larger voids 180 between each tube 120 in a tube bundle
140, as best illustrated in the cross-sections in FIGS. 4-10. The
efficiency of heat exchange between the tube-side fluid and the
shell-side fluid, via the tube wall, can be further improved over
known heat exchangers by a swirl flow created by the twisted
segments of tubes 120 and the voids 180. Specifically, the swirl
flow can be created by a swirling region defined by the individual
tubes 120 of the tube bundle 140, and generally comprising the
voids 180 along the twisted sections. The shell-side fluid can
travel between the voids 180, and the varying space defined
thereby, and generally along the length of the tubes 120 and tube
bundle 140. In this way, the shell-side fluid can be acted upon by
the tubes 120 depending on the orientations thereof relative to
segment S, as best depicted in FIGS. 4-10, to create a swirl effect
in the shell-side fluid, which can produce a swirl flow.
[0029] Further, because a twisted section 154 is generally adjacent
to an at least one straight section 152, wherein the tubes 120 of
the tube bundle 140 are generally arranged in a tighter arrangement
with fewer and smaller voids between the tubes, the overall
mechanical resonance of the tube 120 is not adversely affected by
the spacing and voids 180 of the twisted section 154. The
intermittent twisted segments 154 can support the tubes 120 and
tube bundles 140 within the shell in a manner that provides a
highly flexible support system with enhanced heat transfer on the
tube- and shell-side flows, such that each tube 120 or tube bundle
140 is generally self-supporting, even without the use of baffles.
Such support can be achieved, at least in part, by the twisted
segments 154 which can produce tube-to-tube spaced-apart contact
points 170 between adjacent tubes 120, while also defining the
voids 180 discussed herein, with each individual tube 120 being
secured in place by adjacent tubes 120, and facilitating securement
of adjacent tubes 120. Such arrangement can reduce vibration and
promote easier cleaning on the shell-side through the heat
exchanger 100.
[0030] It is important to note that the present inventions (e.g.,
inventive concepts, and so on) have been described in the
specification and/or illustrated in the FIGURES of the present
patent document according to exemplary embodiments; the embodiments
of the present inventions are presented by way of example only and
are not intended as a limitation on the scope of the present
inventions. The construction and/or arrangement of the elements of
the inventive concepts embodied in the present inventions as
described in the specification and/or illustrated in the FIGURES is
illustrative only. Although exemplary embodiments of the present
inventions have been described in detail in the present patent
document, a person of ordinary skill in the art will readily
appreciate that equivalents, modifications, variations, and so on
of the subject matter of the exemplary embodiments and alternative
embodiments are possible and contemplated as being within the scope
of the present inventions; all such subject matter (e.g.,
modifications, variations, embodiments, combinations, equivalents,
and so on) is intended to be included within the scope of the
present inventions. It should also be noted that various/other
modifications, variations, substitutions, equivalents, changes,
omissions, and so on may be made in the configuration and/or
arrangement of the exemplary embodiments (e.g., in concept, design,
structure, apparatus, form, assembly, construction, means,
function, system, process/method, steps, sequence of process/method
steps, operation, operating conditions, performance, materials,
composition, combination, and so on) without departing from the
scope of the present inventions; all such subject matter (e.g.,
modifications, variations, embodiments, combinations, equivalents,
and so on) is intended to be included within the scope of the
present inventions. The scope of the present inventions is not
intended to be limited to the subject matter (e.g., details,
structure, functions, materials, acts, steps, sequence, system,
result, and so on) described in the specification and/or
illustrated in the FIGURES of the present patent document. It is
contemplated that the claims of the present patent document will be
construed properly to cover the complete scope of the subject
matter of the present inventions (e.g., including any and all such
modifications, variations, embodiments, combinations, equivalents,
and so on); it is to be understood that the terminology used in the
present patent document is for the purpose of providing a
description of the subject matter of the exemplary embodiments
rather than as a limitation on the scope of the present
inventions.
[0031] It is also important to note that according to exemplary
embodiments the present inventions may comprise conventional
technology (e.g., as implemented and/or integrated in exemplary
embodiments, modifications, variations, combinations, equivalents,
and so on) or may comprise any other applicable technology (present
and/or future) with suitability and/or capability to perform the
functions and processes/operations described in the specification
and/or illustrated in the FIGURES. All such technology (e.g., as
implemented in embodiments, modifications, variations,
combinations, equivalents, and so on) is considered to be within
the scope of the present inventions of the present patent
document.
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