U.S. patent number 3,628,590 [Application Number 04/877,954] was granted by the patent office on 1971-12-21 for air cooler having multiple cooling coils.
This patent grant is currently assigned to American Standard Inc.. Invention is credited to George R. Knebusch.
United States Patent |
3,628,590 |
Knebusch |
December 21, 1971 |
AIR COOLER HAVING MULTIPLE COOLING COILS
Abstract
An air cooler comprising two parallel finned heat exchange coils
acutely angled to the direction of airflow and located within a
rectangular duct housing, each coil having a drain trough at its
downstream edge. By angling the coils it is possible to provide
greater total fin face area, a lower air velocity through the
coils, a higher heat transfer, and less pressure drop in the
airstream.
Inventors: |
Knebusch; George R. (North
Olmsted, OH) |
Assignee: |
American Standard Inc. (New
York, NY)
|
Family
ID: |
25371079 |
Appl.
No.: |
04/877,954 |
Filed: |
November 19, 1969 |
Current U.S.
Class: |
62/330; 62/285;
62/288; 62/426; 165/122; 62/290; 62/286; 62/298; 165/101 |
Current CPC
Class: |
F24F
1/0007 (20130101); F24F 13/22 (20130101) |
Current International
Class: |
F24F
13/00 (20060101); F24F 1/00 (20060101); F24F
13/22 (20060101); F25d 021/14 () |
Field of
Search: |
;165/101,122,125
;62/285,286,290,426,272,288,289,291,305 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Wye; William J.
Claims
I claim:
1. An air cooler comprising a rectangular air duct which includes
two parallel duct sidewalls defining the general path flow through
the duct; a partition generally midway between and parallel to said
duct walls for subdividing the duct into two separate duct sections
having transverse dimensions a ; finned heat exchange coil in each
duct section; each coil taking an acute angle to the flow axis of
the respective duct section; and each coil spanning substantially
the entire dimension a between the respective partition and duct
sidewall; the aforementioned angularity of each coil being such
that each coil has a length b in the direction of flow which is
appreciably greater than the duct section dimension a; said coils
extending en general parallelism with one another at approximately
the same angle to the aforementioned duct sidewalls; the duct being
constructed so that the air is caused to flow through each duct
section in the same direction; the partition acting as a flow
splitter to subdivide a single incoming airstream into two separate
component streams flowing through the two coils in parallel flow
relationship to one another.
2. The air cooler of claim 1 wherein the duct is adapted for
horizontal airflow disposition; said coils being sloped downwardly
in the direction of the duct outlet; each coil having a drain
trough subjacent the end thereof closest to the duct outlet for
receiving condensate flowing downwardly along the fin trailing
edges.
3. The air cooler of claim 2 and further comprising a connector
tube interconnecting the two drain troughs so that condensate is
able to drain from one trough to the other.
4. The air cooler of claim 2 wherein the partition takes the form
of a first tray operable to receive condensate from the upstream
face of the overhead coil; the combination further comprising a
second try operable to receive condensate from the upstream face of
the lowermost coil; each tray being pitched slightly from the air
inlet to the air outlet so as to empty into the respective drainage
trough.
5. The air cooler of claim 4 wherein each drain trough is
essentially a U-shaped channel mechanism having its mouth facing an
end edge of its respective coil; each coil having a thickness
dimension c and each trough having a mouth dimension d which is
somewhat greater than dimension c whereby the air duct is adapted
for vertical airflow disposition, either upflow or downflow, such
that the troughs continue to retain their condensate-trapping
capabilities.
Description
THE DRAWINGS
FIG. 1 is a transverse sectional view taken through an air cooler
formed under the invention.
FIGS. 2 and 3 are fragmentary sectional views taken on lines 2--2
and 3--3 in FIG. 1.
FIG. 4 through 6 are schematic views showing the FIG. 1 cooler
operatively associated with other components to make up various
different air conditioner assemblies.
The cooler 10 shown in FIG. 1 comprises a boxlike housing having a
top wall 12 and bottom wall 14 connected at their four corners by
vertical pillars 16. FIG. 2 shows two of the pillars; similar
pillars would be provided at the remaining two corners of the box.
The space between the two illustrated pillars 16 is occupied by a
vertical panel 18 having insulation 20 adhered to its inner face. A
similar panel may be provided between the other two nonillustrated
pillars 16. One or more of the panels 18 can be removably connected
to the pillars, as by screws, to provide side access to the
interior of the duct formed by the boxlike housing.
As shown in FIG. 1 the duct may be arranged to have airflow
therethrough in the directions denoted generally by numeral 22. The
duct is subdivided into two separate duct sections by means of a
partition 24 which extends across the entire width of the housing
as measured in the arrow A direction (see FIG. 2). The space above
partition 24 forms one air duct section, and the space below
partition 24 forms a second separate duct section.
Each duct section contains a finned heat exchange coil 26 having a
suitably number of coolant tubes 28 and plate-type fins 30. The
drawings show each heat exchanger as having one row of tubes 28,
but in practice each heat exchanger is preferably equipped with
three rows of tubes. The plate-type fins 30 are in the plane of the
paper in FIG. 1 so that the air flows between the parallel fins in
moving from each space 32 to each space 34. The fins are suitably
spaced, as for example 14 fins per inch, and the fins are angled
with respect to the flow axis of each dust section so that the
length b of each heat exchanger is appreciably greater than the
transverse dimension a of each duct section. Preferably the
angularity of each coil is about 25.degree., and the length of the
housing is such that dimension b is approximately twice as great as
dimension a. This permits housing 10 to be formed as a boxlike
structure having a generally square configuration but having a
total coil face area that is substantially greater than can be
provided by coils arranged in upright dispositions.
CONDENSATE REMOVAL
During service the air flowing across the fins is cooled by the
relatively cold fluid (water or vaporizable refrigerant) flowing
through tubes 28. Moisture in the entering airstream is condensed
out of the air and flows downwardly along the trailing edges of the
fins 30. Ultimately this moisture is discharged into one of two
drain troughs 38 which extend the full width of the airspace
(dimension A). Each trough is essentially a U-shaped channel
mechanism closed at its opposite ends but having an open mouth
portion facing the end edges of the respective heat exchange coil
26 the mouth of each trough has a dimension d that is somewhat
greater than the thickness of the coil as measured by dimension c.
Therefore the air box 10 can have different gravitational
orientations without hampering the condensate-trapping capability
of the two troughs 38. Thus, the box can be arranged for horizontal
airflow as shown in FIG. 1, or the box can be arranged for downflow
application or upflow application as will be apparent hereinafter,
without interfering with the action of the trough.
It will be noted from FIG. 1 that partition 24 has a slight
angularity with respect to the duct axis, the partition being
pitched slightly downward from front to rear, i.e., in the
direction of trough 38. The lateral edges of partition 24 are
turned upwardly as at 27, so that the partition serves as a tray
for conducting condensate in the arrow 29 direction into the trough
38.
Condensate can form in each of the spaces 32 when coils 25 are
direct expansion coils utilizing vaporizable refrigerant. In such
applications the liquid refrigerant lines, refrigerant dryer,
refrigerant suction line, refrigerant expansion valve, etc. can be
disposed within the box in space 32. These refrigerant devices are
relatively cold and have a tendency to condense moisture out of the
entering airstream; the moisture gravitates into the tray formed by
partition 24. Additional moisture can also form on the outer
surface on the return bends 40 for each of the coils. FIG. 2 shows
one return bend, but it will be appreciated that a large number of
bends are necessary to interconnect the straight portions of the
tubes 28. These return bends are arranged above the space
circumscribed by the upper tray 24 or the lower tray 24a, both
trays being essentially the same construction, and each leading to
one of the troughs 38. The general arrangement is such that trays
24 and 24a are adapted to convey liquid condensate into their
respective drain troughs 38.
As shown in FIG. 1, the upper drain trough 38 is connected to the
lower trough via a hollow connector tube 42. Thus, moisture
collected in the upper trough gravitates through tube 42 into the
lower drain trough 38 and ultimately through a discharge opening 44
formed by the short discharge pipe 46.
COIL SUPPORT
The coil and condensate disposal assembly can be mounted within box
10 by various different support mechanisms. As shown in FIGS. 1 and
2, the coils are mounted in generally cantilever fashion from two
upright angle irons 48, only one of which is visible in the
drawings. Each angle iron 48 is suitably welded to a rear one of
the pillars 16, and each angle iron extends the full housing
height. Each angle iron 48 carries two generally triangular side
sheets 50 and 52, each side sheet having an inturned flange 54
which is suitably bolted to a flange 55 on the tube sheet 60 of the
respective coil 26. Each coil is therefore suspended from two
triangular side sheets, said sheets serving to channel the outlet
airstream through the box outlet. Such an arrangement prevents
airflow around the ends of the respective coils, thereby insuring
that essentially all of the air passes through the fin areas.
AIR COOLER ACTION
As previously noted, the coils have lengths b that are appreciably
greater than the duct section dimensions a. The face area of each
coil is accordingly appreciably greater than the duct
cross-sectional area as defined by dimension a. Because of the area
relation the air is caused to appreciably decelerate as it enters
each coil; also the air is diffused along the face of the coil. The
air having a relatively low linear velocity has a relatively long
transition time in the fins so that the air is able to give up a
substantial portion of its heat content to the fins and to the
fluid in tubes 28.
It would be possible to increase the fin transition time of the air
by using upright heat exchangers having deeper fins (dimensions c)
and a greater number of rows of tubes. Thus finned coils having as
many as eight rows of tubes are commercially obtainable. However
such deep coils increase the lengths of the narrow air passages
between the fins, and thus appreciably increase a larger blower,
which increases space requirements and also noise emission. The
illustrated arrangement, using two coils inclined or angled with
respect to the direction of airflow, is advantageous in that heat
transfer is achieved without large pressure drops or high linear
air velocities.
The relatively low air velocity means a reduced carryover of
moisture in the outlet stream. Assuming the air cooler is arranged
for horizontal airflow application, the moisture tends to flow
downwardly along the trailing edges 36 of the fins and into the
trough 38. Some of the moisture tends to be reintrained by airlift
action, but because the air velocity is relatively low the tendency
toward reintrainment is lessened.
The reintrainment problems encountered in conventional units
usually requires that the drain pan extend for a suitable distance
beyond the coil to trap sufficient numbers of airborne droplets.
With the illustrated drain trough design the condensate collection
mechanism can be shorter with consequently reduction in the
front-to-rear reduction of the housing.
AIR COOLER DISPOSITION
The FIG. 1 air cooler can be used in various duct systems as show
in FIGS 4, 5 or 6. As shown in FIG. 5, the duct system includes a
filter box 70, the previously described cooler 10, a blower box 72,
and duct-type electric heater 74 having resistance heater elements
(not shown) extending across the duct 74 space. This type of system
may be used in a horizontal position within a crawl space or other
space having a small vertical clearance. The vertical dimension of
the duct sections 70, 72 and 74 can be relatively small because
cooler 10 employs inclined air cooler coils.
FIG. 4 illustrates the FIG. 5 assembly with certain components
juxtaposed and arranged for downflow application. In such an
application the FIG. 1 cooler would be arranged so that walls 12
and 14 would be disposed vertically. The air would flow downwardly,
and in the same general pattern as by arrows 22. The troughs 38
would be disposed in the lower areas of the housing, and condensate
would collect in both troughs. The pipe 42 would continue to
conduct liquid from one trough to the other. Condensate would be
discharged through pipe 46.
FIG. 6 illustrates the system of components arranged for upflow
application. In such an application cooler 10 would be disposed
with its walls 12 and 14 vertical, and with drain troughs 38 at the
lower end of the housing. The air would flow in a direction reverse
to that indicated by arrows 22, in which case the fin edges 36
would be the leading edges and fin edges 35 would be the trailing
edges. Condensate forming on edges 35 would flow into trays 24 and
24a and thence into the troughs 38 via the spaces between the
fins.
* * * * *