U.S. patent number 3,575,387 [Application Number 04/781,348] was granted by the patent office on 1971-04-20 for air control damper for evaporative heat exchangers.
This patent grant is currently assigned to Baltimore Aircoil Company, Inc.. Invention is credited to Wilson E. Bradley, Jr., Edward N. Schinner.
United States Patent |
3,575,387 |
Bradley, Jr. , et
al. |
April 20, 1971 |
AIR CONTROL DAMPER FOR EVAPORATIVE HEAT EXCHANGERS
Abstract
This application discloses a blow-through air fan for
evaporative heat exchangers having a diffusion duct containing a
moveable damper and a cooperating fixed baffle so that in the full
flow position little resistance to air is offered and in the
maximum choke position the air pressure across the mouth of the air
discharge duct is sufficiently uniform to prevent aspiration of
water.
Inventors: |
Bradley, Jr.; Wilson E.
(Ellicott City, MD), Schinner; Edward N. (Silver Spring,
MD) |
Assignee: |
Baltimore Aircoil Company, Inc.
(Baltimore, MD)
|
Family
ID: |
25122431 |
Appl.
No.: |
04/781,348 |
Filed: |
December 5, 1968 |
Current U.S.
Class: |
261/30; 261/64.1;
55/418; 261/111 |
Current CPC
Class: |
F28F
25/10 (20130101); F28F 25/12 (20130101); F04D
27/0253 (20130101); F04D 29/462 (20130101); F28C
1/02 (20130101); Y02B 30/70 (20130101); F05D
2250/52 (20130101) |
Current International
Class: |
F28F
25/10 (20060101); F28F 25/12 (20060101); F28F
25/00 (20060101); F04D 29/46 (20060101); F28C
1/00 (20060101); F28C 1/02 (20060101); B01d
047/00 () |
Field of
Search: |
;261/(C.T.),30,64.3,111
;55/418 ;230/114 (B)/ |
References Cited
[Referenced By]
U.S. Patent Documents
|
|
|
2374130 |
April 1945 |
Planiol |
3169575 |
February 1965 |
Engalitcheff, Jr. et al. |
|
Primary Examiner: Miles; Tim R.
Assistant Examiner: Maikowitz; Steven H.
Claims
We claim:
1. In an evaporative heat exchanger having a sump for receiving
water gravitating from a heat exchange region, a wall partially
defining said sump, a centrifugal blower located outside said sump,
air ducting surrounding said blower, passing through said wall and
presenting an air discharge mouth within the sump, the improvement
that comprises, a damper located in said ducting, means mounting
said damper for movement from a full open position in which it lies
substantially parallel to the air flow in the region where it is
located to a maximum choke position in which it passes at least one
stream of air and means downstream of said damper to modify the
direction of said airstream to distribute the air across the full
cross section of the ducting mouth evenly enough to prevent water
aspiration.
2. The improvement of claim 1 in which the means downstream of said
damper is a stationary guide.
3. In an evaporative heat exchanger having a sump for receiving
water gravitating from a heat exchange region, a sloping wall
partially defining said sump, a centrifugal blower located outside
said sump, air ducting surrounding said blower, passing through
said wall and presenting an air discharge mouth within the sump,
the improvement that comprises, a damper located in said ducting on
the same side of said sloping wall as said centrifugal blower,
means mounting said damper for movement from a full open position
in which it lies substantially parallel to the air flow in the
region where it is located to a maximum choke position in which it
passes at least one stream of air and means downstream of said
damper to modify the direction of said airstream to distribute the
air across the full cross section of the ducting mouth evenly
enough to prevent water aspiration.
4. In an evaporative heat exchanger having a sump for receiving
water gravitating from a heat exchange region, a sloping wall
partially defining said sump, a centrifugal blower located outside
said sump, air ducting surrounding said blower, passing through
said wall and presenting an air discharge mouth within the sump,
the improvement that comprises, a damper located in said ducting on
the same side of said sloping wall as said centrifugal blower,
means mounting said damper for movement from a full open position
in which it lies substantially parallel to the air flow in the
region where it is located to a maximum choke position in which it
passes at least two streams of air and means downstream of said
damper to modify the direction of at least one of said streams to
promote the merging of said streams by the time the mouth of the
ducting is reached.
5. The improvement of claim 4 in which the means downstream of said
damper is a stationary guide which in the full open position of the
damper lies parallel to the air flow from the blower.
6. The improvement of claim 5 in which the means downstream of the
damper is on the same side of said sloping wall as said damper.
7. The improvement of claim 4 in which the means downstream of said
damper is a pair of rods extending across the airstream.
8. The improvement of claim 7 in which the pair of rods are located
on the sump side of the plane of the sloping wall partially
defining said sump.
9. The improvement of claim 4 in which said damper extends for the
full width of said ducting and is curved as viewed in cross
section.
Description
This application relates to blow-through type evaporative heat
exchangers and, more particularly, to improved equipment for
controlling the flow of air to the heat exchange region of such
heat exchangers.
Evaporative heat exchangers are devices in which air and water are
flowed in countercurrent or other contact relation through a heat
exchange region. A small portion of the water is evaporated, and
the heat of vaporization is extracted from that which is to be
cooled. For example, in the case of a cooling tower evaporation of
some of the water cools the rest; in an evaporative condenser,
evaporation of water extracts heat from the refrigerant. Equipment
of this type is extensively used in the heat dissipation phases of
air conditioning, industrial cooling and refrigeration. The
equipment functions using outside air. Outside air is, of course,
subject to temperature variations; and the equipment is subject to
variations in the heat load with which it is required to deal.
Thus, on a cool day with a full heat load or on a warm day with a
light heat load or a combination of both, the equipment has an
excess of cooling capacity. To reduce the amount of cooling
capacity to meet a low load and/or cool air condition, a usual
procedure is to reduce the amount of air flow through the heat
exchange region. For very complete control the air flow should be
capable of being greatly reduced, for example by as much as 80 to
90 percent.
In blow-through type heat exchangers as shown in U.S. Pat. No.
3,132,190 to Engalitcheff, this air control function has been
successfully accomplished by the use of a damper located in the air
ducting between the centrifugal fan and the sidewall of the pan
section of the equipment. One type of damper which has been used
successfully in this environment is shown in U.S. Pat. No.
2,719,666 to Hollingsworth et al.
Recently, there has been developed an improved type of evaporative
heat exchanger in which the sump or pan section, that is, the lower
portion of the equipment which receives the water as it falls from
the heat exchange region, is made in the form of a V. Equipment of
this type is shown and described in application Ser. No. 706,003,
filed Feb. 16, 1968 now U.S. Pat. No. 3,442,494. While the use of
the V-section sump has numerous advantages such as reduced water
inventory, reduced weight, greatly facilitated shipping capability,
and so forth, a consequence of the use of the V-sump is that the
ducting for the air blowers is required to be both substantially
shorter and differently arranged than was the case with the
blow-through evaporative heat exchanger having sumps of
conventional configuration. It has been found, for example, that
the conventional damper as disclosed in said Hollingsworth U.S.
Pat. No. 2,719,666 has a tendency to cause water leakage into the
ducting around its operating shaft and to cause the fan duct to
aspirate water if it is located inside the sloping plane of the
sump wall of the V-type unit and, even if moved outside that wall
still causes aspiration of water and additionally interferes with
air flow when the damper is in the maximum flow position. Because
of the substantially shorter length of the diffusion ducting
between the outlet of the centrifugal blowers and the plane of air
discharge within the sump, the eddy currents which are produced by
the damper create regions of pressure at the mouth of the air duct
which are negative relative to the sump pressure resulting in
aspiration of water into the fan region to the detriment of its
performance and durability.
It is an object of the present invention to overcome the foregoing
deficiencies and to provide an air control damper which is
characterized by negligible interference with fan efficiency in the
full open position and yet is capable in its maximum choke position
of reducing the air output to almost a full cutoff without causing
aspiration of water into the fan housing.
Furthermore, according to the present invention the damper may be
controlled and moved through the full range of positions from a
full open position to a maximum choke position under conditions
which avoid aspiration of water into the fan housing through the
mouth of the air fan duct as well as shaft leakage problems.
Other objectives 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 vertical section of a cooling tower having a V
sump of the type shown in application Ser. No. 706,003, filed Feb.
16, 1968, now U.S. Pat. No. 3,442,494, incorporating an improved
air control damper constructed in accordance with the teachings of
the present invention;
FIG. 2 is a fragmentary view in vertical section to an enlarged
scale of the centrifugal blower, ducting and damper incorporated in
the cooling tower of FIG. 1, the damper being shown in the full
open position;
FIG. 3 is a view in vertical section and to an enlarged scale
illustrating the maximum choke position of a damper of the type
shown in FIG. 1;
FIG. 4 is a fragmentary view in vertical section to an enlarged
scale of a modified type of damper constructed in accordance with
the teachings of the present invention, the damper being shown in
the maximum choke position and the full open position being
indicated in broken lines; and
FIG. 5 is a fragmentary view in section taken on the line 5-5 of
FIG. 4.
Referring now to the drawings in greater detail, FIG. 1 illustrates
a cooling tower of the type disclosed and claimed in application
Ser. No. 706,003, filed Feb. 16, 1968 now U.S. Pat. No. 3,442,494.
This cooling tower comprises a water spray section 10 below which
are located heat exchange regions 11 occupied with fill functioning
to present a large surface area for water-air contact. Below the
fill region there is an air distribution region 12 and below that
is the sump 13. The sump 13 is defined by two triangular vertical
walls 14, one of which shows in FIG. 1, a vertical, rectangular
wall 15 and a sloping wall 16. The walls 14, 15, and 16 define, in
effect, a trough having a cross section in the form of a V.
A centrifugal blower 17 is located beneath the sloping wall 16 of
the sump 13 and air ducting 18 connects the outlet of the housing
of the blower 17 with the interior of the sump region 13. The
ducting 18 terminates at a mouth 19 which lies within the sump 13
above the level of water therein.
Briefly stated, the function of the apparatus of FIG. 1 is to
extract heat from water. To this end, water which is to have heat
extracted from it is introduced into the cooling tower at a header
20 from which there extend a large number of spaced parallel pipes
21 covering the cross-sectional area of the region 10. Each pipe 21
is fitted with a plurality of nozzles 22 and from the various
nozzles 22 water is discharged to gravitate through regions 11 and
12 and into the sump 13. As the water falls through the regions 11
and 12, it is contacted by counter flowing air moving upwardly from
the fan mouth 19 through the cooling tower. The air-water contact
causes evaporation of some of the water and the latent heat of
vaporization is extracted from the remainder of the water resulting
in cooling of the same. Mist eliminators 23 function to prevent the
upflowing air from driving mist out of the top of the cooling
tower. The water from which heat has been extracted is collected in
the bottom of the sump and is withdrawn through a conduit 24 to a
point of use. To replace water losses caused by evaporation and
blow down, makeup water is added to the system as needed by
conventional means, not shown.
The sump is provided with a baffle at 25 to stabilize the water
level against the influences of the withdrawal of water and the
impingement of air on the upper surface of it. A baffle 26 is
located in the region 12 and functions to assist in distributing
air uniformly across the cross section of the cooling tower.
The fill region 11 is made up of modular units which are disclosed
and claimed in application Ser. No. 706,004, filed Feb. 16, 1968.
For purposes of the present invention, it suffices to say that a
large number of curved metal pieces 27 are arranged in mutually
spaced relation to provide an air-water path therebetween.
The present invention is concerned with the controlling of the flow
of air from the centrifugal blower 17 and better to describe this
function, reference is made to FIGS. 2 and 3. FIG. 2 shows the
blower 17 to a much enlarged scale and in that FIG. most of the
remaining structure of the cooling tower is omitted for convenience
of illustration. The blower 17 is of the centrifugal type having a
center air inlet at 28 and blades 29 which discharge the air into
the blower housing 30. The blower housing 30 is of generally
rectangular cross section defined by two vertical walls 31 (one of
which shows in FIG. 2) connected by a curved wall 32 which is
contoured to provide a region of increasing cross-sectional area
between the cutoff at 33 and the fan housing discharge region which
is roughly a straight line from the cutoff 33 to the upper end of
the fan housing at 32a. The air discharge duct 18 is supported from
sloping wall 16 of the sump 13 and provides a continuing ducted air
path of rectangular cross section between the end of the fan
housing 30 and duct mouth 19 which is located within the sump area.
Note that the discharge end of the fan housing 30 telescopes into
the ducting 18. Some additional diffusion occurs between the end of
the fan housing and the mouth 19 of the ducting 18 so that the air
issuing from the ducting 18 has had some of the energy which has
been put into it by the blower 17 converted from dynamic to static
form.
Under normal conditions of operation, the air issuing from the
mouth 19 of ducting 18 would flow to the mouth in a direction
generally as indicated by the arrows in FIG. 2. There are
conditions, however, when the heat load is low or when the ambient
air is cool or both when the unit has overcapacity which makes it
desirable to operate the cooling tower with a reduced flow of air.
To this end, there is provided in the housing ducting 30 on the
opposite side of the plane of the wall 16 from the mouth 19, a
sheet metal damper 34 made of a curved piece of metal 34a and a
chordwise piece 34b connected to an operating shaft 35 which passes
through the walls 31 to a point where angular displacement of the
shaft 35 can be initiated. Note that shaft 35 lies outside the sump
region and hence does not require to be sealed against water
leakage. In FIG. 3 the damper 34 is shown in the maximum choke
position and in that position the output of the air from the mouth
of the ducting 18 is reduced by as much as 80 to 90 percent. At the
same time the air output presents a substantially even pressure
front across the mouth of the ducting 18 positive with respect to
the sump pressure so that even in the maximum choke condition, the
fan is protected against aspiration of water. This is accomplished
by so locating and arranging the damper 34 that in the maximum
choke position there is space for air flow at both ends of the
damper, these spaces being indicated at regions 36 and 37 in FIG.
3. Thus, the air to the right of the damper 34, as it is viewed in
FIG. 3, is divided into two streams by the damper, one issuing
through space 36 and the other issuing through the space 37. A
stationary baffle 38 is located downstream of the axis of the
damper 34 and this baffle acts to subdivide the stream issuing
through the space at 37 to promote better distribution of the air
across the cross section of the duct 18. In effect, the streams
passing through regions 36 and 37 are caused to merge enough before
the mouth 19 of duct 18 is reached so that an even enough pressure
front is presented to prevent water aspiration.
The damper 34 is so shaped and located as to offer virtually no
interference to the air flow when it is in the FIG. 2 position.
This is also true of the baffle 38 which extends between the walls
33 of the air duct in a plane substantially parallel to the plane
of the air issuing from the blades of the blower. Thus, in the FIG.
2 position neither the baffle 38 nor the damper 34 offers
resistance to air flow of any appreciable magnitude. When baffle 34
is in the FIG. 3 position, however, it tends to drive the air back
into the impeller blades 29 greatly to decrease the output of the
blower. Furthermore, the air which does pass through the space at
37 is not moving in the same direction as is the case when the
damper 34 is in the FIG. 2 position so that now the baffle 38 forms
a stream dividing function. For convenience of construction ducting
18 and blower housing 30 may be made as shown in FIG. 2. However,
any construction can be used so long as a continuous ducting
surrounds the blower rotor, extends through the sump wall, and
terminates in a discharge mouth within the sump region.
In FIG. 4 there is shown a modified damper constructed in
accordance with the teachings of the present invention but again
offering negligible resistance to the air flow in the open position
but permitting, in the maximum choke position, as much as 80 to 90
percent reduction in air flow. In this case, the ducting and blower
are much the same as those described in FIGS. 1 to 3, inclusive,
except that the blower rotor 40 is of larger capacity and hence of
larger diameter and therefore has to be placed with its periphery
closer to the sloping sump wall 41 than is the case with blower
rotor 28 and sump wall 16. This requires that the blower housing 42
as well as the air discharge ducting 43 inside the sump wall be
differently contoured. As is the case with the FIG. 2 construction,
the particular arrangement of the sheet metal is not the important
thing but rather the resulting ducting which the air issuing from
the blower sees in its travel from the rotor to the discharge
mouth. In this instance, a damper 44 made of two sheet metal pieces
44a and 44b is fixed to rotate with a shaft 45 which extends
through the sidewalls 46 of the fan housing 42. The damper 44 is
movable from the full open broken line position to the maximum
choke full line position of FIG. 4 by operation of the shaft 45. As
was the case with damper 34 there is an air passage at 47 between
the damper 44 and the outer curved wall 48 of the fan housing 42,
and there is another space 49 between the other end of the damper
and the periphery of the rotor 40. Again, in the maximum choke
position, two air streams are produced and again the stream issuing
through the space 49 is directionally modified by a stationary
baffle. In this case, however, the baffle is in the form of two
rods 50 and 51 which extend between the sidewalls 52 and 53 of
ducting 43, see FIG. 5. Again, the air streams are distributed so
that there is a substantially positive pressure front across the
ducting 43 at its mouth 54.
The invention may be embodied in other specific forms without
departing from the spirit or essential characteristics hereof. The
embodiment and the modification described are therefore to be
considered in all respects as illustrative and not restrictive, the
scope of the invention being indicated by the appended claims
rather than by the foregoing description, and all changes which
come within the meaning and range of equivalency of the claims are
therefore intended to be embraced therein.
* * * * *