U.S. patent application number 13/856749 was filed with the patent office on 2014-10-09 for cooling tube included in aircraft heat exchanger.
The applicant listed for this patent is Hamilton Sundstrand Corporation. Invention is credited to Michael Doe, Matthew William Miller, Irving C. Ostrander, Brian R. Shea, Kurt L. Stephens, Michael Zager.
Application Number | 20140299303 13/856749 |
Document ID | / |
Family ID | 51653646 |
Filed Date | 2014-10-09 |
United States Patent
Application |
20140299303 |
Kind Code |
A1 |
Doe; Michael ; et
al. |
October 9, 2014 |
COOLING TUBE INCLUDED IN AIRCRAFT HEAT EXCHANGER
Abstract
A channel tube includes a body having first and second surfaces
extending between first and second opposing ends to define a tube
width. The first and second surfaces are separated from each other
by a distance defining a tube height. A plurality of ports extend
through the body and between the first and second surfaces to
define a fluid path extending in a direction of the tube width.
Each port defines a plurality of walls and a plurality of ribs
having a thermal conductive surface to transfer heat therethrough.
A first wall extends in a direction of the tube width. The second
wall extends in a direction of the tube width and is disposed
opposite the first wall. At least one rib is integrally formed
between the first and second walls and extends perpendicular
thereto.
Inventors: |
Doe; Michael; (Southwick,
MA) ; Shea; Brian R.; (Windsor, CT) ;
Stephens; Kurt L.; (Windsor Locks, CT) ; Zager;
Michael; (Windsor, CT) ; Miller; Matthew William;
(Enfield, CT) ; Ostrander; Irving C.;
(Springfield, MA) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Hamilton Sundstrand Corporation |
Windsor Locks |
CT |
US |
|
|
Family ID: |
51653646 |
Appl. No.: |
13/856749 |
Filed: |
April 4, 2013 |
Current U.S.
Class: |
165/177 |
Current CPC
Class: |
F28F 1/022 20130101;
F28D 2021/0021 20130101; F28D 7/1615 20130101; F28D 7/1684
20130101; F28D 7/1653 20130101 |
Class at
Publication: |
165/177 |
International
Class: |
F28F 1/00 20060101
F28F001/00 |
Claims
1. A channel tube included in a heat exchanger, comprising: a body
including first and second surfaces extending between first and
second opposing ends to define a tube width, outer surfaces of the
first and second surfaces separated from each other by a distance
defining a tube height; and a plurality of ports extending through
the body and between the first and second surfaces to define a
fluid path extending in a direction of the tube width, each port
defining a plurality of walls and a plurality ribs having a thermal
conductive surface to transfer heat therethrough, the plurality of
ribs comprising: a first wall extending in a direction of the tube
width; a second wall extending in a direction of the tube width,
the second rib wall disposed opposite the first wall; and at least
one rib integrally formed between the first and second walls and
extending perpendicular thereto.
2. The channel tube of claim 1, wherein the first wall, the second
wall and the at least one rib are formed integrally to one another
and define a port thickness that determines a heat transfer rate of
liquid flowing through the port.
3. The channel tube of claim 2, wherein the first and second ends
include a curved portion extending radially from the body of the
tube.
4. The channel tube of claim 3, wherein the body consists of
fourteen ports.
5. The channel tube of claim 4, where the ports are
rectangular-shaped to define a port height-to-port width ratio.
6. The channel tube of claim 5, wherein the at least one rib has a
width of 0.010 inches.
7. The channel tube of claim 6, wherein the first and second walls
have width of 0.014 inches.
8. The channel tube of claim 7, wherein the port has height of
0.100 inches and a width of 0.0594 inches.
9. The channel tube of claim 8, wherein the tube height is 0.128
inches.
10. The channel tube of claim 9, wherein the body, the first and
second walls and the at least one rib are integrally formed from a
thermal conductive material.
11. The channel tube of claim 10, wherein the thermal conductive
material is aluminum.
12. The channel tube of claim 3, wherein the width of the curved
portion is 0.020 inches.
Description
BACKGROUND
[0001] The present inventive concept relates generally to a heat
exchanger, and more particularly, to a cooling tube included in a
jet aircraft heat exchanger.
[0002] Commercial jet aircrafts typically include a one or more
galley areas having one or more cooling compartments where food and
beverages are stored. The cooling compartments include cooling
units to control the temperature within the compartment.
Accordingly, the food and beverages stored in the cooling
compartment may be cooled.
[0003] The galley cooling unit includes a heat exchanger to remove
heat from within the compartment. For example, hot circuit air
flows across an outer surface of tubes containing a cooled liquid
coolant. Conventional heat exchangers, such as a liquid-to-air heat
exchanger, include one or more cooling tubes to flow liquid
therethrough. Heat from within the compartment may be transferred
to the liquid flowing through the cooling tubes. The heat of the
liquid is ultimately removed and rejected from the aircraft using
an additional fluid conditioning system. The shape of the cooling
tube may control the amount of heat removed from the liquid, i.e.,
the heat transfer rate, and the fluid pressure drop across the heat
exchanger.
SUMMARY
[0004] According to one embodiment of the present inventive
concept, a channel tube includes a body having first and second
surfaces extending between first and second opposing ends to define
a tube width. The first and second surfaces are separated from each
other by a distance defining a tube height. A plurality of ports
extend through the body and between the first and second surfaces
to define a fluid path extending in a direction of the tube width.
Each port defines a plurality of walls and a plurality of ribs
having a thermal conductive surface to transfer heat therethrough.
A first wall extends in a direction of the tube width. The second
wall extends in a direction of the tube width and is disposed
opposite the first wall. At least one rib is integrally formed
between the first and second walls and extends perpendicular
thereto.
BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS
[0005] The subject matter which is regarded as the inventive
concept is particularly pointed out and distinctly claimed in the
claims at the conclusion of the specification. The forgoing and
other features of the inventive concept are apparent from the
following detailed description taken in conjunction with the
accompanying drawings in which:
[0006] FIG. 1 is a plan view of a heat exchanger according to an
embodiment;
[0007] FIG. 2 is an exploded view of the heat exchanger illustrated
in FIG. 21; and
[0008] FIGS. 3 and 4 are a cross-sectional view of a channel tube
according to at least one embodiment.
DETAILED DESCRIPTION
[0009] Referring to FIGS. 1 and 2, a heat exchanger assembly 100 is
illustrated according to an embodiment. The heat exchanger assembly
100 includes inlet 102 that receives a liquid coolant and an outlet
104 that outputs heated liquid. The core 106 includes a tube
assembly 108 defining a liquid circuit. The tube assembly 108
comprises a plurality of layers 110. According to at least one
embodiment illustrated in FIG. 2, the tube assembly 108 has
twenty-eight layers 110. Each layer 110 comprises a plurality of
channel tubes 112. In at least one embodiment, each 110 layer
includes three channel tubes 112. One or more of channel tubes 112
may include a plurality of ports 114 that form a fluid path
extending along the width of the channel tube 112, as discussed in
greater detail below. An air fin 116 may be interposed between each
layer 110 to promote the transfer of heat to the liquid flowing
through the channel tubes 112.
[0010] The channel tubes 112 deliver the liquid coolant from the
inlet 102 to the outlet 104. The liquid coolant may comprise a
mixture of approximately 60 percent (%) of propylene glycol and 40%
water. Air may interact with the heat exchanger assembly 100
through air fin 116 such that heat is transferred from the air to
the liquid coolant, thereby cooling the air. The heated liquid
flows through the channel tubes 112 undergoing three passes in a
cross-counter flow configuration in the process before exiting
through outlet 104. Heat may be removed from the liquid cooling
loop by downstream equipment.
[0011] Referring now to FIGS. 3 and 4, a cross-sectional view of a
channel tube 112 is illustrated according to an embodiment. The
channel tube 112 includes a body having a first surface, e.g., a
top surface 118, and a second surface, e.g., a bottom surface 120.
The top and bottom surfaces 118, 120 extend between first and
second opposing ends 122, 124 to define a tube width. In at least
one embodiment the channel tube has a tube width ranging from
approximately 0.995 inches (approximately 2.527 centimeters) to
approximately 1.003 inches (approximately 2.548 cm), a tube height
(HT.sub.TUBE) ranging from approximately 0.125 inches
(approximately 0.318 cm) to 0.130 inches (approximately 0.330 cm),
and a tube length (L.sub.TUBE) ranging from approximately 14.0
inches (approximately 35.56 cm) to approximately 15.0 inches
(approximately 38.1 cm). The body of the channel tube 112 is formed
integrally from a single thermal conductive material including, but
not limited to, 31104 aluminum, and may be formed, for example,
using an extrusion process. The first and second ends 122, 124 may
include a radius of curvature that ultimately forms a curved nose
portion 126. The curved portion 126 extends radially from the body
of the channel tube 112 to support and protect the channel tube
ends 122, 124 from exterior contact, and while also absorbing fluid
pressure exerted on the ends by flowing liquid. The curved nose
portion may have a width (W.sub.END) of approximately 0.020 inches
(approximately 0.051 cm).
[0012] The plurality of ports 114 are formed through the body of
the channel tube 112 and between the top and bottom surfaces
116,118. Each port 114 extends along the width of the channel tube
112 to convey liquid between the inlet 102 and the outlet 104 of
the heat exchanger 100. In one embodiment, the ports 114 are
approximately square-shaped. In at least one embodiment, the
corners of the ports 114 may be curved to form a square with
rounded corners. Alternatively, the ports 114 are
rectangular-shaped to define a port height-to-port width ratio. The
port height-to-port width ratio may be expressed as port
height/port width=ratio. In at least one embodiment, the port
height-to-port width ratio is expressed as 0.100 inches/0.0594
inches=1.6835 inches).
[0013] In at least one embodiment, the curved ends 122, 124 may
define an adjacent port 114 having a semi-circular shape. The width
of the semi-circular-shaped end ports (W.sub.SEMICIRC) are
approximately 0.0594 inch (0.150876 cm). The end ports have a
radius of curvature.
[0014] Each port 114 defines a first wall, e.g., a top wall 128, a
second wall, e.g. a bottom wall 130, and at least one rib, e.g., a
center rib 132. The center rib 132 is formed between each adjacent
port 114 and extends between the top and bottom walls 128,130. The
top and bottom walls 128, 130 have a height (HT.sub.TOP,
HT.sub.BOTTOM) of approximately 0.014 inches (approximately 0.036
cm). In at least one embodiment, the center rib 132 has a width
(W.sub.CENTER) of approximately 0.010 inches (approximately 0.0254
cm). The center rib 132 is not limited to the aforementioned width,
and may have a width ranging from approximately 0.0085 inches
(approximately 0.0216 cm) to approximately 0.0115 inches
(approximately 0.0292 cm). The top wall 128, bottom wall 130, and
center rib 132 are formed integrally to one another. Accordingly,
dimensions of the walls and ribs define the overall thickness of
each port 114. The number of walls and ribs, width of the port,
height of the port, rib thickness, wall thickness, tube material
controls the rate of heat transferred to the liquid from the air
circuit of the heat exchanger. That is, the rate at which heat is
added to the liquid flowing at a set flow rate may be controlled by
varying each of the described tube dimensions (rib thickness, wall
thickness, tube width, number of ports, port width, port height)
independent of modifications to the parameters on the air circuit
of the heat exchanger. Accordingly, the channel tube 112 may be
sized to meet system performance and pressure drop requirements. In
at least one embodiment, the ports 114 have a width (W.sub.PORT) of
approximately 0.0594 inches (approximately 0.150876
cm+/-tolerances) and a height (HT.sub.PORT) of approximately 0.100
inches (approximately 0.254 cm+/-tolerances).
[0015] The plurality of walls and ribs provide a heat transfer
surface, which contacts the liquid flowing through the ports 114.
Accordingly, heat is transferred from the liquid through the walls
and ribs and out of the channel tubes 112. The rate of heat
transfer from the channel tube 112 and the pressure realized by the
heat exchanger 100 may be controlled based on the number of ports
114. Reducing the number of ports 114 (e.g., providing 10 ports)
reduces the secondary heat transfer area of each tube 112 and
decreases the fluid pressure drop, while increasing the number of
ports 114, (e.g., providing 18 ports) increases the secondary heat
transfer area and increases the fluid pressure drop. Therefore, the
heat transfer primary and secondary surface area and fluid pressure
drop provided by the channel tube 112 may be controlled based on
the number of ports 114 and the design of the corresponding ribs
and wall thicknesses, number of ports, the port height, and the
port width.
[0016] While various embodiments of the inventive concept had been
described, it will be understood that those skilled in the art,
both now and in the future, may make various modifications to the
embodiments which fall within the scope of the claims which follow.
These claims should be construed to maintain the proper protection
for the invention first described.
* * * * *