U.S. patent number 3,598,179 [Application Number 04/758,812] was granted by the patent office on 1971-08-10 for heat exchanger.
Invention is credited to Louis F. Giauque.
United States Patent |
3,598,179 |
Giauque |
August 10, 1971 |
HEAT EXCHANGER
Abstract
The invention provides a heat exchanger comprising first and
second rows of vertically arranged tubes, the outlets of the tubes
in each row being connected to separate condensate headers, to
which separate traps are connected, and the steam inlets of the
second row of tubes being connected to the steam outlets of the
first row of tubes whereby the tubes of the first row are
automatically purged and air binding is prevented.
Inventors: |
Giauque; Louis F. (Kapuskasing,
Ontario, CA) |
Family
ID: |
25053216 |
Appl.
No.: |
04/758,812 |
Filed: |
September 10, 1968 |
Current U.S.
Class: |
165/111; 165/145;
165/113; 165/122; 165/176; 165/DIG.222 |
Current CPC
Class: |
F28D
21/0008 (20130101); F24D 5/00 (20130101); F24D
19/087 (20130101); F28B 1/06 (20130101); Y10S
165/222 (20130101); F28B 2001/065 (20130101) |
Current International
Class: |
F24D
19/08 (20060101); F24D 19/00 (20060101); F24D
5/00 (20060101); F28D 21/00 (20060101); F28B
1/00 (20060101); F28B 1/06 (20060101); F28b
001/06 (); F28b 009/08 (); F28b 009/10 () |
Field of
Search: |
;165/110,111,176,175,112,113,143,144,145,122 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
|
|
|
|
|
|
|
117,442 |
|
Sep 1943 |
|
AU |
|
354,689 |
|
Feb 1930 |
|
GB |
|
Primary Examiner: Davis, Jr.; Albert W.
Claims
What I claim as my invention is:
1. Apparatus for passing steam in heat exchange relation with air
having an initial temperature below the freezing point of water,
said apparatus comprising a plurality of exchanger tubes arranged
in first and second rows, the second row being arranged behind the
first row and each heat exchanger tube having a steam inlet and a
steam outlet, means for directing a stream of air across the
exterior surfaces of the tubes so that the air passes across the
tubes of the first row before passing across the tubes of the
second row, means to supply steam to the steam inlets of the tubes
of the first row for flow therethrough, means to connect the steam
outlets of the tubes of the first row to the steam inlets of the
tubes of the second row, and separate first and second trap means
to prevent escape of steam but to discharge condensate, the tubes
of the first row being connected to said first trap means and the
tubes of the second row being connected to said second trap
means.
2. Apparatus according to claim 1, including a first header to
which the steam inlets of the first row of tubes are connected and
a second header to which the steam inlets of the second row of
tubes are connected.
3. Apparatus for passing steam in heat exchange relation with air
having an initial temperature below the freezing point of water,
said apparatus comprising a plurality of vertically extending heat
exchanger tubes arranged in first and second rows, the tubes of the
second row being arranged behind the tubes of the first row and
each tube having a steam inlet and a steam outlet, means to direct
a stream of air substantially horizontally across the exterior
surfaces of the tubes so that the air passes across the tubes of
the first row before passing across the tubes of the second row,
means to supply steam to the steam inlets of the tubes of the first
row for flow therethrough, means interconnecting the steam outlets
of the tubes of the first row with the steam inlets of the tubes of
the second row, separate first and second condensate headers
connected to the steam outlets of the tubes of the first row, and
the tubes of the second row, respectively, the first and second
condensate headers being isolated from one another, first and
second traps to prevent escape of steam but to discharge
condensate, first conduit means interconnecting the first
condensate header and the first trap, and second conduit means
interconnecting the second condensate header and the second trap,
said first and second conduit means being isolated from one
another.
4. Apparatus according to claim 3, including a first header to
which the steam inlets of the first row of tubes are connected and
a second header to which the steam inlets of the second row of
tubes are connected.
5. Apparatus according to claim 1, in which the tubes are
horizontal and are stacked vertically one upon the other in each
row, the tubes extending between a first vertically extending
header, to which the steam outlets of the first row of tubes and
the steam inlets of the second row of tubes are connected, and
second and third vertically extending headers to which the steam
inlets of the first row of tubes and the steam outlets of the
second row of tubes are respectively connected, said first trap
means being connected to said first header, and said second trap
means being connected to said third header.
Description
BACKGROUND OF THE INVENTION
This invention relates to heat exchange apparatus, and is concerned
particularly with apparatus for passing steam in heat exchange
relation with air having an initial temperature below the freezing
point of water; such apparatus is commonly called blast coil or
heater coil apparatus.
It is known to employ steam to heat air for use in the heating of
buildings such as factories, aircraft hangars and the like. One
form of apparatus used for heating the air comprises two or more
rows of heat exchanger tubes arranged one behind the other; steam
is passed through the tubes from a common steam header, the air
being propelled across the exterior of the tubes by means of a fan,
and the condensate being collected in a common condensate header.
The exteriors of the tubes are normally encircled with fins, either
integral with the tubes or wound on, to increase the rate of heat
transfer from the hot tubes to the cooler air. It has been found
that, under certain conditions of airflow when the air is initially
at a temperature below the freezing point of water, the condensate
which forms in tubes of the row of tubes with which the air first
comes into contact, freezes and bursts the tubes. A row of tubes
with which the air first comes into contact is hereinafter called a
"first row." Air at a sufficiently low temperature to cause
bursting of the tubes as described above is commonly encountered in
the winter in, for example, the northwesterly parts of the United
States and most of Canada, and the invention is particularly
concerned with providing heat exchange apparatus which may be used
in such northerly regions and which prevents, or at least
minimizes, the freezing of condensate in the tubes.
Although the makers of heat exchanger tubes realize that a freezing
problem exists in connection with heating very cold air, they have
been unable to provide a satisfactory solution. So called
"nonfreezing" or "steam-distributing" heating tubes which are
presently on the market comprise an outer finned tube, within which
is concentrically arranged an inner tube, and a clearance is
provided between the outer surface of the inner tube and the inner
surface of the outer tube. The wall of the inner tube is perforated
all along the length and steam is supplied to the inner tube and
passes through the perforations into the clearance between the
tubes. This construction is intended to prevent the condensate from
freezing in the tubes but it is not sufficiently effective for this
purpose in apparatus having more than one row of tubes connected to
a common condensate header. Moreover, such "nonfreezing tubes" cost
approximately one-third more than conventional heat exchanger
tubes.
Freezing may be prevented by using excessive amounts of steam e.g.
bypassing steam through the tubes without restriction, but this is
not practical in the majority of installations where steam is an
expensive commodity; likewise, disposal of the noncondensed steam
poses a problem.
In my U.S. Pat. No. 3,074,479 entitled HEAT EXCHANGE APPARATUS,
issued Jan. 22, 1963, I have described a form of apparatus which
goes a long way towards solving the problem of the freezing of
condensate in the tubes of the first row in a twin or multiple-row
heat exchanger. The solution, which does not require the use of any
excess steam, is to provide means to eliminate the leg of
condensate which normally builds up and freezes in each tube of the
first row when this row is connected with a subsequent row or rows
to a common header at the condensate ends. This is achieved by
allowing the pressure drop of the steam across the tubes of the
first row to be independent of the pressure drop across the tubes
of the other row or rows. For this purpose separate first and
second traps to prevent escape of steam but to discharge condensate
are connected respectively to the tubes of the first row and the
tubes of the second row.
The construction described in the above mentioned patent overcomes
the problem of condensate hangup, or condensate leg formation, in
the first row of tubes, and thereby eliminates a major cause of
freezing. However, there are other factors which can lead to
freezing within the first row of tubes, of which the most important
is air binding. It is an object of the present invention to provide
a construction of heat exchange apparatus in which air binding as a
cause of freezing in the first row of heat exchanger tubes is
eliminated.
In the case of a row of heat exchanger tubes connected between a
common steam header and a common condensate header, air binding
will occur if one of the tubes is starved for steam, and the steam
is not perfectly pure. (Even the best commercially produced steam
carries a few p.p.m. of noncondensables). The
"being-starved-for-steam" condition may occur through a peculiarity
of the steam flow from the steam header, or through a greater heat
dissipation from the exterior surface of the particular tube. In
either case the demand for steam in the tube is greater than the
supply from the steam header. Each of the companion tubes will in
such a case supply a little steam to the condensate header together
with air or other noncondensable fluids. This steam and the
noncondensables are fed into the condensate removal end of the
starved tube. In general the point of lowest pressure in a heat
exchanger tube is at its outlet, i.e. where it joins the condensate
header, but for a starved tube the point of lowest pressure is at
some point before the outlet, because the collapse of steam volume
due to condensation creates a pressure drop, which in turn causes
more steam to flow in to take the place of the steam which has
condensed. The starved tube draws in steam from both ends and the
air and noncondensables remain at the point of lowest pressure
within the starved tube. In the course of time, which may be hours
or days, the quantity of air trapped in the starved tube increases,
and the temperature in the area of the steam-air mixture continues
to drop because the partial pressure of the steam becomes less and
less. At the same time the film heat transfer coefficient for the
inside of the tube decreases because of the presence of air, and
finally the inner surface of the tube is cooled to a temperature
below freezing point. Frost builds up rapidly until it bridges the
tube, whereupon condensate rapidly fills up the remainder of the
tube and freezes to burst the tube.
Under high load conditions, and especially in the case of heat
exchanger tubes of relatively small cross section, a condensate leg
can form in a starved tube even when air binding does not occur.
This is because the steam fed back into the tube reaches a high
enough velocity to interrupt the flow of condensate from the
starved tube. The condensate may develop a height to provide the
required suction to draw additional steam from the steam header,
but it can and frequently does, freeze with disastrous results.
Periodic purging of the tubes with excess steam to clear air from
the tubes cannot be carried out satisfactorily because the required
amount of purging varies, because a considerable wastage of steam
is involved, and because disposal of the uncondensed purging steam
is a problem.
According to my invention, the above-mentioned problems are solved
by providing separate steam headers and separate condensate headers
for the first and second rows of heat exchanger tubes, the steam
supply for the heat exchange apparatus being connected only to the
first row steam header. The second row steam header is connected by
plain tubes or conduit means to the condensate header of the first
row of tubes, which may be structurally combined with or separate
from the steam header of the second row, and the condensate headers
are trapped separately as described in my U.S. Pat. No.
3,074,479.
In such an apparatus all the steam for the apparatus is supplied to
the first row of tubes, the amount of steam required by the first
row condensing and being removed; the steam required for the second
row of tubes must also travel through the first row of tubes to the
first row condensate header and from there to the second row steam
header before it can supply the second row of tubes. In this way
the steam purges the tubes of the first row continuously. The most
important function of this design is that it prevents all
possibility of steam being fed back into the tubes of the first row
with consequent air binding, but an incidental advantage is that it
improves the heat transfer rate of the tubes of the first row even
when not air bound.
BRIEF DESCRIPTION OF THE DRAWINGS
Preferred embodiments of the invention will now be described by way
of example with reference to the accompanying drawings in
which:
FIG. 1 is a diagram showing the various components of the heat
exchange apparatus according to the invention;
FIG. 2 is an enlarged sectional elevation view of a detail of FIG.
1;
FIG. 3 is a section on line 3- 3 in FIG. 2;
FIG. 4 is an enlarged sectional plan view of a detail of a
modification of the invention;
FIG. 5 is a perspective view, partly broken away, of the heat
exchanger tubes and traps forming part of the apparatus shown in
FIG. 1;
FIG. 6 is a broken away perspective view of one of the traps shown
in FIGS. 1 and 2;
FIG. 7 is a transverse cross section of a heat exchanger coil of
the type used heretofore in installations for heating air by steam.
This view is a sectional elevation as the coil is normally
installed.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring now to the drawings, and particularly to FIG. 1, there is
shown a duct 10 along which cold air is drawn by a fan 11 driven by
an electric motor 12 supported within the duct by struts 13. The
cold air is propelled by the fan through an assembly 14 of heat
exchanger tubes, details of which are illustrated in FIGS. 2 and 3.
The assembly 14 comprises a first row of heat exchanger tubes
indicated at 15 in FIG. 2, and a second row of heat exchanger tubes
indicated at 15: also in FIG. 2. The upper ends of the tubes of the
rows 15 and 15' constitute steam inlets to the tubes and are
connected to steam headers 16, 16', the former being supplied
through inlet 29 with steam from a source or boiler 17 by means of
a steam pipe 18. The bottom ends of the tubes in the first row 15
constitute condensate and steam outlets and are connected to a
first condensate header 19 which is connected by first conduit
means 20' (or 20 as an alternative) to a first steam trap 21. The
steam supplied to header 19 makes its way via conduit means 30 to
second steam header 16. The bottom ends of the tubes of the second
row 15' constitute condensate outlets and are connected to a second
condensate header 22 which is connected by second conduit means 23
to a second steam trap 24. The traps 21 and 24 discharge the
condensate to a hot well or condensate sump (not shown) through
pipe 25.
Referring now to FIG. 5, the arrangement of the rows of heat
exchanger tubes is shown in more detail. The rows of tubes are held
in a rectangular frame made up of channel section side members 26
and channel section upper and lower crossmembers 27. The ends of
the crossmembers 27 are closed by ribs 28. Secured to the underside
of the upper crossmembers 27 and parallel thereto are the steam
headers 16 and 16', the former being provided with a steam inlet
connection 29 secured to the steampipe 18. The upper ends of the
tubes in the rows 15 and 15' are secured in the lower wall of the
steam headers 16, 16'. Except for the ends these tubes are finned
for their full length. The finned tubes in the two rows are all
similar and may be provided with reentrant orifices (not shown) at
their upper ends. Plain transfer tubes 30 are connected at their
lower ends to the condensate header 19, and are connected at their
upper ends to the steam header 16', so that all the steam to the
second row of tubes must have passed through the first row of tubes
and be supplied via the transfer tubes 30.
It will be seen particularly from FIGS. 2 and 3 that the header
assembly at the lower end of the heat exchanger is constructed in
such a manner as to separate steam and condensate discharged from
the first row of tubes. The lower ends of the tubes of the first
row 15 are connected directly to the condensate header 19, which is
a cylindrical pipe lying parallel to the steam header 16. This pipe
communicates with two hollow box structures 19a to which the lower
ends of the transfer tubes 30 are connected. The transfer tubes are
thus connected indirectly to the condensate header 19. Also
communicating with the box structures 19a is a drain 19b which
receives condensate from the header 19. The lower ends of the
finned tubes of second row 15' are connected to the second
condensate header 22, which is of course isolated from the box
structures 19a. The lower ends of the tubes of the second row 15'
are connected to the condensate header 22, which is a cylindrical
pipe having closed ends and lying parallel to the steam header 16'.
The purpose of the drain 19b is to prevent condensate from being
carried over through the transfer tubes 30, but in most practical
applications carryover of condensate does not present a problem and
the drains 19b can be omitted.
The first and second conduit means 20, 23 are connected to the
condensate headers 19, 22 respectively at condensate connections
intermediate the ends of the condensate headers, the first conduit
means 20 actually being connected indirectly to the pipe 19 by
being connected directly to the drain 19b. Upper and lower baffles
(not shown) may be provided to shield the steam headers and the
condensate headers from the full force of the cold air as it passes
across the tubes, substantially as described in my above-identified
U.S. Pat. No. 3,074,479.
Both of the steam traps 21 and 24 are similar and the trap 24 has
been shown in FIG. 6 as illustrative of both traps. The trap
comprises a hollow body 31 having a steam and condensate inlet 32
and a condensate outlet 33; the condensate and steam pass through a
strainer 34 after leaving the inlet 32. A float 35 is secured to an
angle member 36 having side arms 37 which are pivoted to the body
31 at 38. Also secured to the angle member 36 is a bimetallic
element 39 which has secured to one end thereof upstanding lugs 40;
pivoted between the lugs 40 is a bar 41 slotted at 42. Received in
the slot 42 is a rod 43 having a ball 44 at its lower end and
arranged to cooperate with a valve seat 45 at the lower end of an
insert 46. The upper end of the rod 43 is provided with an
adjusting nut 47 having a sleeve portion which is received in the
slot 42. Access plugs 48 are provided in the body and a bracket 49
is secured to the float to control its lowermost position.
The trap is shown in a position it occupies when there is steam in
the trap but no condensate; the steam causes the bimetallic element
to bend and to lift the rod so that the ball 44 comes into contact
with the seat 45 and prevents the escape of steam. When cooler
condensate enters the trap, the bimetallic element straightens and
the float 35 rises to discharge the condensate to the insert 46.
Once the apparatus is in steady operation the float will operate to
maintain a predetermined level of condensate in the trap dependent
on condensate temperature and rate of flow and will discharge the
excess to the hot well. It will be seen that the trap provides
means to prevent the escape of steam but to discharge
condensate.
A modification of the heat exchange apparatus is illustrated in
FIG. 4, which is a view corresponding to FIG. 2 except that it is
primarily for horizontal tube installation, and is therefore drawn
in plan, with steam and condensate connections on the one side.
(FIGS. 1, 2, 5 and 7 represent units designed primarily for
vertical tube installations with top and bottom steam and
condensate connections). Corresponding reference numerals are used
to denote corresponding parts. The essential difference between
this modification and the preceding embodiment is that the steam
inlets of the tubes of the second row 15' are at the far ends of
these tubes and are connected directly to the vertical header 50,
which is in effect a combined condensate header for the first row
and steam header for the second row. The condensate header 51 of
the second row 15' is connected to the near ends of the tubes, and
a trap 24 is connected to this header by a conduit 23. The trap 21
is also at the near end of the assembly, and is connected to the
condensate header 50 by a conduit 52.
Referring now to FIG. 7 there is shown a conventional construction
of heater coil in which freezing readily occurs in the tubes of the
first row. (Once first row tubes freeze, second row tubes soon
freeze also, because of being highly overloaded in comparison to
companion tubes in the same row.) The tubes are held within a
framework and are connected between a common steam header 53 and a
common condensate header 54. A first row of tubes is indicated at
55 and a second row of tubes at 56 and cold air is passed through
the tubes in the direction of the arrow X.
Condensate delivered to the common condensate header 54 leaves
through a conduit 57 and passes to a trap 58 and thence to a hot
well (not shown) through a pipe 59.
Thus, in the conventional apparatus a common steam header and a
common condensate header are provided and the condensate ends of
both rows of tubes are in communication with one another via the
common condensate header. The different demands for steam in the
tubes of the two rows result in differences in the pressure drops
in the tubes with feedback of steam into the tubes of the first
row. (They demand more steam because of heating up colder air than
do the tubes of the second row.) This causes air binding or
formation of condensate legs within the tubes, depending upon
conditions heretofore mentioned. Either one can lead to the
freezing of condensate and the bursting of tubes as explained
previously. This problem is overcome to some extent by providing
condensate headers as described in my above-mentioned U.S. Pat. No.
3,074,479, but condensate often still forms in individual first row
tubes, or air binding takes place, with damaging results to these
tubes. With a construction in accordance with the present
invention, as described above, the tubes of the first row are
continuously purged by the excess steam required for the second
row, and air binding is thereby prevented.
The present invention thus overcomes the problems met with
conventional heating coils in a manner similar to that described in
my above-mentioned U.S. Patent, and additionally eliminates a
further cause of freezing in a convenient and economical
manner.
* * * * *