U.S. patent number 3,784,171 [Application Number 04/820,852] was granted by the patent office on 1974-01-08 for evaporative heat exchange apparatus.
This patent grant is currently assigned to Baltimore Aircoil Company, Inc.. Invention is credited to Axel F. L. Anderson, Wilson E. Bradley, Jr., John Engalitcheff, Jr., Thomas F. Facius.
United States Patent |
3,784,171 |
Engalitcheff, Jr. , et
al. |
* January 8, 1974 |
**Please see images for:
( Certificate of Correction ) ** |
EVAPORATIVE HEAT EXCHANGE APPARATUS
Abstract
A blow-through evaporative heat exchange apparatus having a
blower section with a wet deck section above it. The blower section
has at least one slanting wall to provide space for an electric
motor and blower under the slanting wall. Diffusion means are
provided to ensure a uniform flow of air over the cross section of
the wet deck.
Inventors: |
Engalitcheff, Jr.; John (Gibson
Island, MD), Facius; Thomas F. (Baltimore, MD), Bradley,
Jr.; Wilson E. (Ellicott City, MD), Anderson; Axel F. L.
(Clearwater, FL) |
Assignee: |
Baltimore Aircoil Company, Inc.
(Baltimore, MD)
|
[*] Notice: |
The portion of the term of this patent
subsequent to May 6, 1986 has been disclaimed. |
Family
ID: |
27107608 |
Appl.
No.: |
04/820,852 |
Filed: |
May 1, 1969 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
|
|
706003 |
Feb 16, 1968 |
3442494 |
May 6, 1969 |
|
|
Current U.S.
Class: |
261/29;
261/DIG.11; 261/109; 261/111 |
Current CPC
Class: |
F28F
25/04 (20130101); F28C 1/02 (20130101); F28F
25/087 (20130101); F28F 25/00 (20130101); Y10S
261/11 (20130101); Y02B 30/70 (20130101) |
Current International
Class: |
F28F
25/08 (20060101); F28F 25/00 (20060101); F28F
25/04 (20060101); F28C 1/00 (20060101); F28C
1/02 (20060101); F28d 005/02 () |
Field of
Search: |
;62/305
;261/30,108-113 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
Primary Examiner: Miles; Tim R.
Attorney, Agent or Firm: Stevens, Davis, Miller &
Mosher
Parent Case Text
This application is a division of our copending U. S. application
Ser. No. 706,003, filed Feb. 16, 1968 and now Pat. No. 3,442,494.
Claims
What is claimed is:
1. In a cooling tower having a region of fill, a chamber below said
region, a sloping wall partially defining said chamber, said
sloping wall having a port therethrough, a blower located outside
said chamber and below said wall, means to guide air from said
blower through said port into said chamber, and means including a
curved portion extending adjacent the upper defining edge of said
port into said chamber beyond the plane of said wall, said curved
portion being boxed-in by side walls which also perform an air
guiding function.
2. In a cooling tower having a region of fill, a chamber below said
region, a sloping wall partially defining said chamber, said
sloping wall having a port therethrough, a blower located outside
said chamber and below said wall, means to guide air from said
blower through said port into said chamber, said means including a
curved portion extending adjacent the upper defining edge of said
port into said chamber beyond the plane of said wall.
3. In a cooling tower having a region of fill, a chamber below said
region, a sloping wall partially defining said chamber, said
sloping wall having a port therethrough, means located outside said
chamber below said wall to supply air under pressure through said
port into said chamber, said means including a curved portion
extending adjacent the upper defining edge of said port into said
chamber beyond the plane of said wall.
Description
This invention relates to evaporative type heat exchangers of the
blow through (forced draft), counter-flow type in which air flows
counter-current to the fluid to be cooled or condensed. Although
this description is chiefly concerned with evaporative heat
exchangers of the cooling tower type, it should be understood that
its features and concepts could be adapted to all blow-through
evaporative heat exchangers such as evaporative condensers, liquid
coolers, gas coolers, etc.
In a conventional type "blow through" cooling tower the water to be
cooled is introduced just below mist eliminators through closely
spaced spray nozzles to insure an even distribution across the
entire surface area of the tower. An example of such an arrangement
is disclosed in U. S. Pat. No. 3,198,441 and is hereby incorporated
by reference. The water flows by gravity over a wet deck or fill
material and drops into a sump below.
A fan section, consisting of one or more centrifugal fans, is
fastened to a side wall of the cooling tower and introduces air
into a plenum region, which is located above the sump water level
but below the wet deck section. This plenum region must be of
adequate size so as to allow the air to distribute itself evenly
across the wet deck surface sheets. The fan section is usually a
separate assembly secured to the outside of the cooling tower wall,
thus increasing the overall horizontal width of the tower
substantially.
This invention is directed to a more efficient, compact, and light
weight unit. The fan and drive motor form an integral part of the
pan and sump. There is no substantial extension or protrusion of
the fans beyond the cooling tower side wall. The fan motor and
drive arrangement are protected from direct exposure by the
overhead sloping pan side wall. The sump and plenum is in the form
of an inverted right triangle whose apex forms the bottom of the
sump. Being triangular in shape, the sump water inventory is
greatly reduced with a subsequent reduction in operating weight.
The fan discharges high velocity air through a discharge cowl
located in the sloping side wall of the pan section. This discharge
cowl is situated in the pan section above the sump water level and
below the top of the pan. This type of discharge cowl is disclosed
in U. S. Pat. No. 3,132,190 to Engalitcheff and the disclosure
thereof is hereby incorporated by reference. Due to the compact
design, the discharge cowls are necessarily shorter than those of
the above patent and not as much air expansion can be accomplished
in the cowls themselves, resulting in a somewhat lesser velocity
(kinetic) pressure conversion to static pressure. Additional static
pressure conversion is accomplished in the pan section because its
area gradually expands from the sump water level to the top of the
pan section as will become apparent in the following description.
According to the present invention, it is possible, without loss of
efficiency in the air system, to use a sump of much smaller volume,
with resulting saving in weight by reduction in the volume of
cooled water inventory and saving in plan area or floor space by
locating the fans wholly or partly within the vertical projection
of heat exchange section.
It is an object of the present invention to provide evaporative
heat exchange apparatus that has greater cooling capacity in
proportion to its material weight.
Another object of the present invention is to provide an
evaporative cooler characterized by a reduction in weight resulting
from a decrease in the still water inventory.
A further object of this invention is to provide a more compact
evaporative heat exchanger while maintaining the same cooling
efficiency as in comparable prior art units.
Other objects and advantages of this invention will be apparent
upon consideration of the following detailed description of several
embodiments thereof in conjunction with the annexed drawings
wherein:
FIG. 1 is a view in side elevation of a single module of an
evaporative cooler of the cooling tower type constructed in
accordance with the teachings and principles of the present
invention;
FIG. 2 is a vertical section view of an end elevation of two
modules of FIG. 1 placed back-to-back with a common sump;
FIG. 3 is a side elevation of a multiple fan unit of FIG. 1 placed
end to end;
FIG. 4 is a view in vertical section taken along the line 4--4 of
FIG. 3 showing the air fan construction at a much enlarged
scale;
FIG. 5 is a view in horizontal section taken along the line 5--5 of
FIG. 2;
FIG. 6 is a partial perspective view of the plenum chamber section
showing the baffle angle.
It is to be understood that FIG. 1 illustrates the basic unit of
this invention, where the sump is an inverted right triangle and a
single blower or several blowers on a single shaft driven by a
single motor is located under the hypotenuse of that triangle so
that no substantial projection beyond the superstructure of the
unit is necessary in order to house the motor and blower(s) as has
been necessary in the prior art. This single unit then represents a
basic form of the invention and a basic module which can be
increased in capacity by securing similar units in an end
relationship. Such a multiple unit can then be further increased
increased in capacity by securing similar units "back-to-back" so
that the right triangle sump becomes an inverted isosceles triangle
as depicted in FIG. 2 with a motor and blowers located under each
of the equal sides of that triangle.
When two basic units are secured back-to-back, suitable
modifications are made in the sump and drain fittings so that the
sumps are joined and a common water outlet can be used.
Referring now to the drawings in greater detail and, more
particularly, to FIGS. 1, 2 and 3 thereof, in which the cooling
tower illustrated is comprised of an upper portion 10 (in which the
water is cooled) and a lower sump portion in the form of a V trough
or container 11 in which the cooled water is collected. The upper
portion 10 is rectangular in plan and is made up of a number of
frames superimposed in registry to define four vertical side
walls.
The lower part of sump section 11 has two vertical opposite walls
12 and 13 in the plane of two of the side walls of the upper casing
section and, between them, wall 14 disposed at 45.degree. to the
vertical, convergent and intersecting to define with the walls 12
and 13 the V trough 11. Water to be cooled is supplied through
manifold 16 and issues from various spray nozzles 17 to fall by
gravity through a cooling region containing a wet deck surface
section in the form of a large number of sheet metal elements 18
held by frames in horizontally and vertically spaced relation to
present to the water, in total, a large surface area. The water,
after flowing through the cooling area in contact with the various
sheet metal elements 18 falls by gravity into the V sump 11. This
wet deck section is more fully disclosed in the co-pending
application Ser. No. 706,004 now abandoned entitled "Wet Deck Fill
Section" of the same assignee and filed on even date. Although this
particular section has been illustrated, any wet deck or any
evaporative heat exchange surface can be used in connection with
this invention.
The unit illustrated in FIGS. 1 to 3, inclusive, is provided with
centrifugal blowers which, by means to be hereinafter more fully
described, cause air to flow upwardly between the surface elements
18 counter-current to the gravitating water, whereby some of the
water is evaporated and carried upwardly with the flowing air to
leave the unit through mist eliminators 19 arranged at the top
thereof. Although a centrifugal blower is illustrated, the unit
would operate equally as well with axial flow fans and the term
"blower" as used herein is intended to encompass both. The heat
extracted from the remaining water is, of course, carried with the
exhausting air to the ambient atmosphere. As previously stated, the
cool water falls to the sump. Makeup water enters through valve 20
opened by float 21 (see FIG. 2) and replaces the evaporated water
and any waste water which has been drained to reduce contamination,
etc.
The cooled water is withdrawn from the sump 11 through a conduit 22
and delivered by a pump 23 and conduit 24 to a point of use such as
the heat exchanger schematically shown at 25 in FIG. 3. After use,
the water has taken on heat and must be returned to the cooling
unit for cooling. This return is effected through conduit 26
leading to manifold 16.
Now that the cycling of the water has been described, attention is
called to the effect of the V-bottom sump 11 upon water inventory.
Because the lower portion of the triangular or V-section trough is
of very small volume, only a very little water is held in
inventory, with a decided advantage in reducing weight load on the
supporting area which accommodates the unit.
Not only does the V-bottom of the sump reduce the amount of the
water inventory, but it also, by an arrangement constituting an
important part of the present invention, permits locating of the
blowers substantially within a vertical projection of the
rectangular plan of the upper portion 10 of the unit and because of
its V shape promotes static pressure increase in the sump section.
Of course it is desirable that the fan(s) ae completely under the
sloping wall if possible. However, if a large blower is used due to
particular design requirements, then there may be some projection
beyond the side wall of the unit.
The air distribution for a multiple-blower unit as illustrated in
FIG. 5 is described later in detail. As viewed in FIGS. 2 and 5,
there are two sets of three centrifugal blowers each, a left-hand
set the nearest blower of which bears reference numeral 28, and a
right-hand set the nearest blower of which bears reference numeral
29. Blower 29 and the two blowers 30 and 31 behind it are keyed to
a common drive shaft 32 to which there is also keyed a sheave 33
connected by multiple belts 34 to a drive sheave 35 of an electric
motor 36. Motor 36 is mounted on a base plate 37 slidable in tracks
38. Connected to base plate 37 is a bracket 39 having a threaded
stud 40 passing through it. This stud also passes through a
U-section piece 41 which is the bottom piece of framework of the
blower and motor support system. The stud 40 is provided with nuts
42 by adjustment of which on the stud 40 the motor mount may be
easily shifted and held to control the tension on belts 34.
An arrangement identical to that just described is provided for the
blower 28 and the two blowers behind it. In this case the motor
bears numeral 44, the belt adjusting assembly 45, the belt sheave
46, the common drive shaft 47.
All of the centrifugal blowers, such as blowers 28 and 29, are of
the axial intake, radial discharge type. The individual blowers are
spaced apart, and shaft bearings are located on each end of a group
of blowers. Typical of the construction is the arrangement shown in
FIG. 3, where shaft 32 is provided with a main front bearing at 48
to the left of fan 29 and at the end of shaft 32 remote from the
sheave 33 there is located another main bearing 50. Due to the fact
that an enlarged diameter shaft is used between bearings 48 and 50
only these outboard bearings are required with no bearing between
the blowers on a single shaft. The main bearings 48 and 50 are held
by rigid frame members such as 51 and 52 which extend between
U-section base members 41 and the wall 14. The sides of each fan,
essentially triangular in shape, bear reference numerals 53, 54 and
55. They are arranged in parallel, spaced relationship extending
vertically from the bottom of the unit to the sloping wall 14 of
the pan section. Walls 53, 54 and 55 show in FIG. 3 and, of course,
the front face of an equivalent wall 56 appears on the left side of
FIG. 2. Note that the blowers are held between these vertical walls
in this particular unit, in a position wholly underlying the
sloping walls 14 and 15 of the pan units.
The outlet side of each blower, such as 28 and 29, is connected to
air ducting which passes through the respective sloping wall 15, 14
of the pan section and terminates in a mouth lying nearly in a
vertical plane but sloping slightly in a direction opposite to the
slope of the respective wall 14 or 15 through which the ducting
passes. The ducting associated with blower 29 includes a portion 58
lying wholly within the sump 11. Blower 30 is provided with a duct
portion 59 within the sump and blower 31 with a portion 60. In FIG.
5 portions 61 and 62 within the sump 11 serve the two unnumbered
blowers which lie behind blower 28 as it is viewed in FIG. 2 and
which lie beside it. These duct portions are all of identical
construction, usually of rectangular cross section and therefore
only the ducting for blower 29 will be described in detail.
In FIG. 4, blower 29 is shown to an enlarged scale with side wall
53 cut away to reveal the construction of the ducting from the
cutoff at 63 to the mouth 64 of the interior ducting portion 58.
The total ducted area is defined by wall 53, removed in FIG. 4 for
convenience of illustration, spaced parallel wall 54, a curved wall
located between walls 53 and 54 and extending spirally from the
cutoff 63 through the side wall 14 of the sump to terminate at 66,
flange portion 68 and duct portion 58. Notice that both ends, the
cutoff end at 63 and the end at 66, of the spiral wall 65
telescopes into duct 68 which is fastened by its flanges 68 to the
inner surface of the wall 14 of the V sump 11. The air path defined
by the walls 53, 54 and 65 and the added duct portion 58 and flange
portion 68 is of progressively increasing cross-sectional area in
the direction of air flow, so that a considerable measure of
conversion of velocity pressure to static pressure is accomplished
between the cutoff 63 and the mouth 64 of the ducting system. Note
that the fan 29, as illustrated in FIG. 4, rotates in a
counterclockwise direction.
In the back-to-back unit, the sump or pan section 11, as
illustrated in FIGS. 2, 4 and 5, is centrally divided by a
partition 69 which extends between walls 12 and 13 and from the top
of the pan section downwardly somewhat below the water level of the
sump. Below the lower end of the partition 69 there is located an
air-antientrainment baffle 70 which extends horizontally across the
bottom of the sump above the level of outlet pipe 22. The plate 70
also functions to equalize the withdrawal of water from the sump
11, since it is tapered to present a wider opening for water
passage on the end remote from the outlet. Directly above the
air-antientrainment baffle 70 there can be located a strainer
supported by appropriate brackets.
Upon reference to FIGS. 1, 2 and 5 it can be seen that the air
issuing from the mouths of the various ducts 57 to 62, inclusive,
is directed into a somewhat confined space defined at the bottom by
the water level and in front of the duct mouth by partition 69 and
behind the duct by the sloping wall 14 or 15, as the case may be.
While there is a measure of static pressure increase before the air
leaves the various duct portions 57 to 62, inclusive, yet the
velocity of the air issuing from the mouths of these ducts is too
high for efficient and even air distribution across the cross
section of the fill region which lies above the V-sump section 11.
In the form of the invention illustrated in FIGS. 1 to 4,
inclusive, several means are shown which contribute to the evenness
of the distribution of air across the cross section of the fill.
One of these is the fact that the portion of the sump chamber above
the fan outlet increases in cross-sectional area as the air moves
upwardly from the mouth of the fan duct. This, of course, is due to
the fact that the vertical wall or center partition 69 defines with
the sloping wall 14, in effect, a region in the shape of inverted
right triangle as viewed in vertical section, so that air moving
away from the bottom of the sump and upwardly is necessarily moving
into a region of progressively increasing cross section. This
brings about a measure of static increase in addition to that which
takes place in the discharge ducts.
If, now, reference is made to FIG. 5, it will be observed that the
horizontal spacing between the ducting portions such as duct
portions 57, 61 and 62 on the left side of the unit and 58, 59 and
60 on the right side of the unit is such that the space between the
duct portions is equal to or greater than the width of those
portions themselves. To compute this spacing, it was found
convenient for a unit about 12 feet long to use the following
formula:
spacing between blower equals the length of the sump section minus
with combined width of the blowers in that section divided by the
number of blowers.
This allows a considerable amount of air space between the ducts,
which has been found to contribute importantly to efficiency.
The space between the end fans of a group and the adjacent end wall
of the sump is no less than half the width of the fan ducting.
Arrows in FIG. 5 indicate how a portion of the air, somewhat
baffled by the partition 69, tends to rise toward the top of the
sump in the spaces between the fan ducts.
The air leaving the fan discharge cowls contacts the vertical wall
opposite the cowl opening and some of the air is directed upward
toward the wet deck section. The remainder of the air is turned
180.degree. and fills the space between blowers, as it expands
upward through the V-sump section. The space between blowers should
be so chosen so as to allow the correct proportion of air to enter
and fill this space. It has been found that optimum cooling
capacity is a function of blower width, spacing along the drive
shaft, and the length/width ratio of the V-sump dimensions. For
example, in a particular unit where the sump section was 12 feet
long, 3 22 inches diameter blowers, each 21 inches wide were used
with 27 inches spacing between them and 13 1/2 inches between the
end blowers and the end walls of the sump. Deviation from optimum
blower spacing as previously described, can cause unequal air
distribution which seriously affects the cooling capacity of the
equipment. As the air reaches the top of the V-sump section, its
velocity has been reduced with an accompanying static pressure
gain. For the most part, the air is distributed evenly when it
reaches the top of the V-sump section, however, for a further
refinement in air distribution before reaching the wet deck
section, plenum chamber sections 170 and 71 may be used. These
plenum chambers serve to equalize the small differences in air
velocities leaving the top of the V-sump section.
Thus above the top of the sump section 11 and the lowermost layer
of the fill there may be disposed one or more plenum chamber
sections which are frames each constituting an air distribution
module. The lower module bearing numeral 170 is shown in FIG. 1,
and it can be seen that the unit consists of a rectangular frame
defined by channel members with their flanges facing outwardly, the
side members bearing numerals 73 and 74. Member 73 has secured on
its inside edge an angle member of L section to form angle baffle
77. The horizontal portion of this angle baffle 77 extends
horizontally usually about 2 to 3 inches in length toward the
blower duct. When units are built "back-to-back" as in FIG. 2, the
module 170 is constructed with a central member 75 with angle
baffles 77 extending toward each blower assembly. Frame unit 71 is
in all respects structurally similar to frame unit 170, except that
the angle baffle 77 is omitted.
The effect of the two frames 170 and 71 is to create a large space,
rectangular in plan, above the top of the V trough 11 and below the
wet deck, the function and purpose of said space being to provide a
region to effect more even distribution of the air entering the
fill. The distribution of the air is also greatly improved by angle
baffle 77. Thus the V shape of the trough 11, the provision of
space-defining frames 170 and 71, and the angle baffle 77 all, both
separately and together, contribute materially to the efficiency of
the unit, create a uniform air flow and thus raise the cooling
capacity substantially.
* * * * *