U.S. patent number 3,802,497 [Application Number 05/117,242] was granted by the patent office on 1974-04-09 for heat exchanger for cooling gases.
Invention is credited to Joachim Kummel, Josef Munster, Josef Scharfen, Gert Wellensiek.
United States Patent |
3,802,497 |
Kummel , et al. |
April 9, 1974 |
HEAT EXCHANGER FOR COOLING GASES
Abstract
A heat exchanger for cooling gases and having a number of fire
tubes for conducting hot gases through a cooling chamber whereby
all the tubes will be subjected to substantially the same
conditions with regard to the temperature and flow conditions of a
cooling medium in the cooling chamber.
Inventors: |
Kummel; Joachim
(Castrop-Rauxel, DT), Munster; Josef (Dusseldorf,
DT), Scharfen; Josef (Neuss, DT),
Wellensiek; Gert (Holzhausen/Ammersee, DT) |
Family
ID: |
25758694 |
Appl.
No.: |
05/117,242 |
Filed: |
February 22, 1971 |
Foreign Application Priority Data
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Feb 23, 1970 [DT] |
|
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2008311 |
May 26, 1970 [DT] |
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2025584 |
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Current U.S.
Class: |
165/158;
165/DIG.408; 422/201 |
Current CPC
Class: |
F28F
9/0229 (20130101); F28D 7/106 (20130101); F28F
9/26 (20130101); B01D 51/10 (20130101); F28D
2021/0075 (20130101); Y10S 165/408 (20130101) |
Current International
Class: |
B01D
51/00 (20060101); B01D 51/10 (20060101); F28D
7/10 (20060101); F28F 9/02 (20060101); F28b
009/00 () |
Field of
Search: |
;165/158-162,143,142,156
;23/288M,288L,277R |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Myhre; Charles J.
Assistant Examiner: Streule, Jr.; Theophil W.
Attorney, Agent or Firm: Toren and McGeady
Claims
We claim:
1. A heat exchanger for cooling cracking gases comprising a single
annular row of vertically arranged laterally spaced fire tubes for
conducting hot cracking gases therethrough, first means for
enclosing said row of fire tubes and forming a cooling passageway
for passing a cooling medium over the exterior of said fire tubes,
said first means comprising a vertically arranged jacket laterally
enclosing said row of fire tubes, an upstream floor extending
transversely of and secured to said jacket and the lower ends of
said fire tubes secured to and communicating through said upstream
floor, a downstream floor extending transversely of and secured to
said jacket and the upper ends of said fire tubes secured to and
communicating through said downstream floor, an intermediate floor
extending transversely of said jacket between said upstream and
downstream floors and located adjacent said upstream floor, said
fire tubes extending through said intermediate floor, second means
including a supply pipe for supplying the cooling medium for flow
over said fire tubes, said supply pipe being vertically arranged
and disposed centrally within said row of fire tubes, said supply
tube extending downwardly through said downstream floor and having
its outlet end extending through and terminating at the lower face
of said intermediate floor, said upstream floor intermediate floor
and said jacket forming a cooling medium inlet chamber arranged to
receive the cooling medium from said supply pipe, third means
attached to the lower end of said jacket for introducing hot gases
into said fire tubes and for assuring uniform temperature and flow
conditions in the gases as they flow through said fire tubes in
indirect heat transfer relationship with the cooling medium, said
third means includes a conically shaped baffle located located
centrally on and projecting downwardly from the lower face of said
upstream floor, the diameter of said baffle at said upstream floor
being smaller than the inside diameter of said row of fire tubes,
fourth means forming an annular passage through said intermediate
floor about each said fire tube for conducting the cooling medium
from the cooling medium inlet chamber into the space between said
intermediate and downstream floors for upward flow over said fire
tubes extending therethrough, an overflow pipe extending through
said jacket and communicating with the upper end of the space
between said intermediate and downstream floors for removing the
cooling medium after its upward flow over said fire tubes, and said
fourth means comprises a sleeve-like guide tube located about each
said fire tube and having an inside diameter slightly larger than
the outside diameter of said fire tubes, said guide tube secured to
and extending upwardly from the upper face of said intermediate
floor and said intermediate floor forming an annular opening about
each said fire tube affording communication between the cooling
medium inlet chamber and the annular space between each said guide
tube and said fire tube which it encloses.
2. A heat exchanger, as set forth in claim 1, wherein said third
means for introducing hot gases into said fire tubes includes a gas
supply pipe spaced axially from and below the inlet ends of said
fire tubes, walls forming a closed inlet chamber extending from
said gas inlet pipe to the inlet ends of said fire tubes in the
lower face of said upstream floor, said gas inlet pipe having its
axis disposed centrally of the axes of said fire tubes, said walls
forming the inlet chamber include a frusto-conically-shaped member
connected at its smaller diameter end to said gas inlet pipe and
having its wider diameter end connected to said upstream floor
encircling the outside diameter of said row of fire tubes at their
inlet ends, and said conically-shaped baffle spaced radially
inwardly from said frusto-conically-shaped member and extending
downwardly from said upstream floor for only a portion of the axial
length of said frusto-conically-shaped member.
3. A heat exchanger according to claim 2, in which the conical
widening of said frusto-conically shaped member is such that with a
hot gas pressure of between 1.6 and 1.8 atm.abs., there is produced
a chamber loading which amounts to between 90 and 125
kg/sec./cu.m.
4. A heat exchanger, as set forth in claim 2, wherein the effective
heat-emitting area of the upper face of said upstream floor is at
least twice as large as its effective heat-absorbing area on the
lower face of said upstream floor.
5. A heat exchanger according to claim 4, in which the upstream
floor has said cup-shaped thickening on its side facing a supply
pipe for the cooling medium.
6. A heat exchanger according to claim 4, in which a washing and
drainage outlet is arranged between the upstream flow and the
intermediate floor.
7. A heat exchanger according to claim 1, in which the fire tubes
are formed at least partially at their downstream ends with double
walls.
8. A heat exchanger according to claim 1, in which the fire tubes
are formed with double walls over at most two-thirds of their
length.
9. A heat exchanger according to claim 7, in which the annular
space between inner wall and the outer wall of a fire tube is
filled with air.
10. A heat exchanger according to claim 7, in which the inner wall
of the double walled tube is connected by rolling or welding with
the associated outer wall.
11. A heat exchanger according to claim 7, in which the inner wall
reduces the free throughflow cross-section of the fire tubes by
between 20 and 35 percent.
12. Gas cooling apparatus comprising several heat exchangers
constructed substantially as described with reference to claim 1,
the several heat exchangers being connected in parallel and/or in
series.
13. Apparatus according to claim 12, in which there are at least
two parallel-connected heat exchangers with a common heat exchanger
connected thereafter.
14. Apparatus according to claim 12, in which, in the final heat
exchanger, the fire tubes consist of several tubes of which two
tubes form a double jacket through which cooling medium flows
and/or two tubes form a thermally insulating jacket.
15. Apparatus according to claim 12, in which the heat exchangers
are suspended in a manner enabling them to swing.
16. A plant comprising a furnace for producing hot gases and a
number of pipes which lead the hot gases away from the furnace for
cooling, each of such pipes being connected to a separate heat
exchanger according to claim 1, or to a separate gas cooling
apparatus according to claim 12.
17. A heat exchanger, as set forth in claim 7, wherein the outer
wall of said double wall fire tube is sealed to said means for
enclosing said fire tubes and said inner wall extends out of the
cooling passageway, and a gas collector hood arranged to receive
the end of said inner wall which extends outwardly from the cooling
passageway.
18. A heat exchanger according to claim 17, in which the inner wall
is slidingly arranged in a floor of the gas collector hood and a
heat-proof seal is provided between the floor of the gas collector
hood and the inner wall.
Description
The invention relates to an apparatus for the cooling of fresh
cracking or other gases.
Cracking gases are ordinarily produced at high temperatures and
under appropriate pressure in so-called tube furnaces. Then the
gases must be cooled down in an extremely short time to a
temperature at which a chemical synthesis reaction or re-formation
is no longer possible, that is to say the generated chemical
condition is frozen.
Using conventional heat exchangers, this is effected in that the
fresh cracking gases are conducted through a plurality of
water-cooled tubes, called fire tubes. For reasons of flow-line
pattern and to save space, the known fire tubes are bundled and
arranged as close as possible. Moreover the known fire tubes are
arranged on the inlet side in one common floor and enclosed by a
common jacket.
Between the diameter of the crack pipe conducting the fresh
cracking gas and the external diameter of the bundle of fire tubes
as a rule there is a considerable difference which is compensated
by a suitable funnel-shaped tube piece or a conical widening of the
crack pipe. With the high speed of flow of the cracking gas in
modern production plant, this is the reason for heavy eddying of
the cracking gas upstream of the common floor. As a result of the
ordinarily very incomplete diffusing action of the conical
widening, the flow of cracking gas breaks away in the conical
widening with high speed of flow, and return eddies occur at this
point. The return eddies cause an additional flow resistance and
involved therewith an increased time of sojourn of the cracking gas
before entering the fire tubes, which often is already sufficient
to render a chemical synthesis reaction or re-formation possible
for the cracking gas.
However not only do the return eddies before the common floor of
the fire tubes involve the danger of re-formation of the cracking
gas, but at the same time a varying thermal loading of the fire
tubes and their common floor occurs, the heaviest heating, that is
the heaviest loading, occurring in the centre of the common floor
and in the centre of the bundle of fire tubes. However, at this
point, in the case of water cooling, the cooling action of the
water in the conventional heat exchangers is particularly weak,
since the water supplied in general from the periphery of the
jacket must overcome the flow resistance of many fire tubes in
order to pass into the centre of the bundle and to the centre of
the common floor. There is also the fact that steam bubbles rising
from the common floor and the fire tubes interfere with the water
circulation in the cooling chamber and thus further reduce the
cooling action of the water.
The irregular flow conditions of the water have the result that, at
a temperature below or equal to 570.degree.C and a pH value higher
than or equal to seven, magnetite (Fe.sub.3 0.sub.4) forms on the
water-charged surfaces of the fire tubes which are produced
exclusively from iron. Furthermore, at a temperature greater than
or equal to 570.degree.C and a pH value lower than or equal to
seven, a ferrous oxide (FeO) layer forms on the water-charged
surfaces between the magnetite and the iron of the fire tube wall,
which layer is very brittle and therefore easily chips away
together with the magnetite. Thus the iron of the fire tube wall
again comes directly into contact with the cooling water, and again
magnetite is produced. This corrosion shortens the life of the fire
tubes very considerably and is further reinforced by an
electrochemical corrosion as a result of the different so-called
electric valencies of iron and magnetite and the cooling water
penetrating between the iron and the magnetite.
Moreover due to the chipping magnetite and ferrous oxide in the
middle on the common floor of the fire tubes there are formed
thermally insulating deposits which cause varying floor
temperatures, that is to say in the case of an elevated temperature
in the centre of the floor involve a corresponding distortion of
the floor which in the extreme case leads to damage which puts the
heat exchanger out of action.
The irregular flow conditions of the gas and the high times of
sojourn involved therewith have the result that cracking gas
consisting for example of C.sub.2 H.sub.2 re-forms into C.sub.2
H.sub.6 (ethane) and the free carbon atoms are deposited as a
graphite-type mass on the inner wall of the fire tubes. The
graphite-type mass could per se easily be removed, if in the
cracking gas there were not at the same time constituents with
heavy C-fraction, that is high-boiling hydrocarbons, which as a
result of their high condensation point condense in the case of a
relatively long time of sojourn and likewise are deposited on the
inner wall of the fire tubes. The deposit of free carbon atoms and
of the condensate of the high-boiling hydrocarbons on the inner
wall of the fire tubes then on the one hand diminishes the
efficiency of the heat exchanger. On the other hand the deposits on
the inner wall of the fire tubes, as a result of the now reduced or
deflected cooling of the surfaces and the high inherent temperature
involved therewith, cake with heavy dehydration of the condensed
hydrocarbons into an especially unpleasant increasing dirt coating
(petroleum coke), for the removal of which mostly then a kind of
water spray with a water pressure of 300 atmospheres is
necessary.
With such wearing and soiling phenomena, what is called the tour
time of conventional heat exchangers, used for the cooling of fresh
cracking gas, is correspondingly short.
The invention is therefore based upon the problem of providing an
apparatus for the cooling especially of fresh cracking gases which
ensures a constant uniform cooling effect with any desired
construction size, that is to say gas throughput, gas temperatures
and gas pressure of any desired magnitude.
This is achieved according to the invention, using a heat exchanger
with a number of fire tubes each having substantially the same
cooling effect upon the cracking gas and for this purpose the fire
tubes of the heat exchanger are arranged each in a cooling medium
current which is equal as regards the temperature and the flow
conditions. This results in a relative limitation of the number of
fire tubes, which together with the arrangement of the fire tubes
characteristic for the equal cooling action, surprisingly also
leads to the existence of equal flow conditions for the cracking
gas in all fire tubes.
Favourable operating conditions are present in the case of an
annular arrangement of the fire tubes and supply of the cooling
medium through a central descending pipe. In the extreme case a
limitation of the number of fire tubes to one row of fire tubes is
provided here. From the one row of fire tubes then arranged in a
circle it is clear that the necessary equal operating conditions
are obtained for all fire tubes. This includes both equal cooling
conditions due to overall equal flow resistance opposing the flow
of the cooling medium, and equal gas flows in the fire tubes. The
equal gas flows in the fire tubes in the case of circular
arrangement of the fire tubes, and the ordinary hot gas inlet
widening conically towards the fire tubes, is explained by the fact
that the flow conditions in the inlet are substantially
rotation-symmetrical in relation to the central axis. The inlet
openings of the circularly arranged fire tubes are charged from a
gas supply aligned with the fire tubes only with gas of equal flow
behaviour, so that with equal tube dimensions and surface qualities
in the fire tubes, equal flow conditions establish themselves.
The rotation-symmetrical flow conditions in the widening of the gas
supply circuit may be assisted by a baffle which is situated in the
inlet upstream of the fire tubes. The baffle is preferably made
conical and adapted in such a way to the widening, that is to say
fills the widening to such extent, that the latter with a gas
pressure of 1.6 to 1.8 atm.abs. produces a chamber loading which
amounts at maximum to 125 mg/sec/cu.m and at least 90
kg/sec/cu.m.
As a result of its relatively large volume and its form adapted to
the inlet, the baffle directs the gas directly into the fire tubes
and thus advantageously prevents the return eddies which occur in
conventional cracking gas supply systems, so that diffusor angles
between 60.degree. and 100.degree. easily become possible for the
conical widening of the gas inlet. This property makes the baffle,
irrespective of the particular arrangement of the fire tubes,
likewise suitable for conventional gas supply conduits and cooling
devices for gas.
However the displacement body is also particularly advantageous for
cooling devices with fire tubes which are retained at their inlet
ends in one common upstream floor. In this case the baffle has the
additional effect that it imparts to the upstream floor a larger
heat-emitting area than heat absorbing area and thus
extra-ordinarily good cooling. For this purpose the baffle is
preferably so formed that the heat-emitting area of the upstream
floor is at least twice as large as its heat absorbing area.
Furthermore the baffle reinforces the common floor of the fire
tubes in such a way that it can be extremely thin. In this case a
bending resistance is imparted to the upstream floor which prevents
unacceptable bulging out of the floor under the action of the
cooling medium pressure and on heating. Optionally a cup-shaped
thickening of the floor on its side facing the coolant supply pipe
will contribute to this bending resistance. Apart from increasing
the bending resistance, the thickening of the floor then has the
additional advantage that it improves the distribution of the
cooling medium, issuing from the supply pipe, to the individual
fire tubes.
The equal cooling effect upon the fire tubes is kept constant by an
unambiguous and stable circulation of the cooling medium. As
cooling medium there serves according to choice liquid lead, liquid
sodium and especially water in natural circulation. For the cooling
with water in natural circulation the fire tubes, as known per se,
are held at their inlet ends and at their outlet ends in common
upstream and downstream floors and with an intermediate floor which
encloses the coolant supply pipe and is spaced from the upstream
floor. The intermediate floor may conduct the cooling medium
issuing from the supply pipe against and according to choice over
the entire upstream floor and/or in case of need even to a
particular extent upon heavily heated surfaces of the upstream
floor.
The intermediate floor may provide guide tubes which surround each
fire tube in the region of maximum heat-flux density. The guide
tubes ensure that the rising cooling medium flows securely along on
the fire tubes and intensively cools them. Moreover, when the fire
tubes are arranged upright with their inlet ends lowermost, the
guide tubes together with the intermediate floor form dirt pockets
in which scale and the like impurities can collect, so that these
are not deposited in thermally insulating manner on the upstream,
that is the lower, floor.
The dirt pockets are of such size that their cleaning is not
necessary during what is called the tour time of the apparatus. As
well as the dirt pockets, according to choice a regular washing off
of the interspace between the upstream floor of the fire tubes and
the intermediate floor is optionally also provided, in order to
prevent deposits on the upstream floor and thus deterioration of
the heat transmission to the cooling water. Then a washing and
water drain-off system is arranged between the lower floor and the
intermediate floor for the washing.
The fire tubes may be formed over a part of their length as double
walled tubes, the cavity between the inner and outer walls being
sealed off both against the cooling medium and against the hot gas.
Thus the thermal conductivity in the tube wall of the fire tubes,
with appropriate formation and arrangement of the double wall, is
reduced to such an extent that the temperature of the internal wall
lies above the maximum occurring condensation point of the gas,
while the temperature of the outer wall lies substantially below
the temperature pertaining to the maximum condensation point, and
depositing of gas leading, say, to petroleum-coke separations is
prevented. With the formation as double walled tubes there is
optionally at the same time also involved a reduction of the free
throughflow cross-section in the fire tubes, which then preferably
amounts to 20 to 35 percent and in the end part of the fire tubes
effects as regards the gas a higher throughflow of mass, that is to
say advantageously opposes soiling of the fire tubes.
Each cooling device according to the invention, especially in the
case of only one row of fire tubes arranged in circular form, has a
limited cooling performance which is taken into consideration in
modern cracking gas generators such for example as pyrolysis
furnaces by a parallel connection of several heat exchangers. This
has the additional advantage that the inflowing cracking gas is
distributed to the individual heat exchangers and thus the flow
conditions are already favourably influenced.
Along these lines, in contrast to conventional pyrolysis furnaces
or the like cracking gas generators having several tubes which
conduct away the so-called moist cracking gas, each of these tubes
is provided with at least one heat exchanger. In the case of
delivery quantities of 3,000 to 8,000 kg/h per tube, each tube is
preferably provided with four heat exchangers connected in parallel
with one another and together forming a cooler section. Moreover a
horizontal or especially slightly inclined arrangement of the fire
tubes is optionally foreseen. The horizontal and slightly inclined
arrangement permits, for example in the case of pyrolysis furnaces,
of setting up the entire apparatus for the cooling of the fresh
cracking gas, hereinafter called cracking gas cooler, beneath the
cracking furnace. Furthermore the horizontal arrangement of the
fire tubes is much simpler in production and maintenance than a
vertical arrangement.
In the case of the use of water in natural circulation and the
deliberate generation of steam to boost the cooling effect and the
natural circulation, in the approximately horizontal arrangement of
the fire tubes a separation of the steam-water current is prevented
by the fact that the fire tubes are provided each with a double
jacket through which the cooling water flows. Thus its own cooling
water forced circulation is advantageously allocated to each
individual fire tube.
A further development of the apparatus according to the invention
consists in the provision of at least two series-connected heat
exchangers with a gas exit temperature of below 500.degree.C. for
the first heat exchanger. In this case the construction style of
the second heat exchanger is of subordinate importance, for below
500.degree.C the cracking gas no longer reforms, so that several
heat exchangers connected in parallel can be provided with one
series-connected common heat exchanger, and this may possibly also
take place even in the case of an over-long time of sojourn of the
cracking gas in the series-connected heat exchanger. In this case
however precipitation of the cracking gas in the series-connected
heat exchanger is prevented in that the thermal conductivity of the
fire tubes of the series-connected heat exchanger is reduced, at
least in the exit region, by the use of a thermally insulating
double jacket, in such a way that the temperature on the inner wall
of the fire tube lies above the maximum condensation point of the
cracking gas, even in the case of a temperature on the outer wall
of the fire tubes lying below the minimum cracking gas condensation
point.
Some examples of apparatus constructed in accordance with the
invention are illustrated in the accompanying drawings,
wherein:
FIG. 1 shows the overall side view of an apparatus;
FIG. 2 shows a partial elevation, partial longitudinal section, of
the apparatus of FIG. 1;
FIG. 3 is a section taken on the line III--III in FIG. 2;
FIG. 4 is a section showing a fire tube of another apparatus;
FIG. 5 is a section taken on the line V--V in FIG. 1;
FIG. 6 shows in diagrammatic representation a part of an overall
production plant for cracking gas;
FIG. 7 shows the fire tube of a third apparatus;
FIG. 8 shows a fourth apparatus for the cooling of fresh cracking
gases having several parallel-connected heat exchangers and one
series-connected common heat exchanger, in plan view;
FIG. 9 shows the apparatus according to FIG. 8 in a view in the
direction IX--IX in FIG. 8; and,
FIG. 10 shows a heat exchanger according to FIG. 8 in an individual
view.
In FIGS. 1 and 5 a cooling apparatus is shown which consists of
four heat exchangers 1 connected in parallel with one another. The
heat exchangers 1 are at the same time arranged three-dimensionally
parallel with one another and connected with one another through
lugs 2 and bolts 22 at two positions lying one above the other in
each case, for assembly. In the operational condition the heat
exchangers 1 are suspended on suitable connectors, cables or the
like devices and the lower bolts 22 are released in each case, so
that the heat exchangers 1 with adequate freedom of movement are
mounted for swinging in the upper lugs 2 and bolts 22. Thus
displacements and variations of dimension of the heat exchangers
occurring as a result of thermal expansion are very simply
compensated.
For the connection with the connectors or cables the heat
exchangers 1 are provided in the upper and especially in the lower
region with tie-bolts 23. The arrangement of the tie-bolts 23 in
the lower region here has the advantage that on heating the heat
exchangers expand upwards and thus bending of the transfer conduits
leading to the heat exchangers 1, which are subject to a
substantially higher thermal stressing than the transfer conduits
leading away from the heat exchangers 1, is prevented.
The four heat exchangers 1 together form a so-called cooler
section. According to FIG. 6, in a pyrolysis furnace 24 generating
a cracking gas, to each so-called cracking gas pipe 25 conducting
away cracking gas there is allocated a cooler section. The fresh
cracking gas is here fed within a cooler section to the heat
exchangers 1 at a temperature of between 830.degree. and
850.degree.C and a pressure of between 1.6 and 1.8 atm.abs. by way
of a distributor device 3 and pipes 4 from the associated cracking
gas pipe 25.
The distributor device 3 consists of an inlet flange 6 which is
connected with a corresponding flange 5 of the cracking gas pipe
25, and of a dome 7 adjoining the inlet flange 6 and connecting the
pipes 4 with the inlet flange 6.
The pipes 4 open or widen into gas-distributor cones 8. The gas
distributor cones 8 terminate according to FIG. 2 in each case in a
cylindrical recess 9 of a container 10 and are connected with the
container 10 in sealed manner by means of a sealing ring 11 and a
bellows 12, which at the same time has the task of compensating
thermal expansions and possibly also production tolerances. The
bellows 12 is here connected with a conduit 21 which conducts away
the so-called leakage gas which penetrates past the sealing ring 11
into the bellows 12.
The container 10 consists essentially of a tubular pressure jacket
13, two floors 14 and 15 and five to twelve cooling pipes,
designated as fire tubes 16, which as shown in FIG. 3 are arranged
in uniform distribution with one another, parallel with the
longitudinal axis of the container 10 and in circular form. The
fire tubes 16 are welded into the floors 14 and 15 so that the
cracking gas flowing out of the associated distributor cone 8 flows
through passage holes 17 of the floor 14, which connect the fire
tubes 16 with the distributor cone 8, into the fire tubes 16 at the
rear end, in the direction of flow, of the container 10.
In this action a uniform flow of the cracking gas into the fire
tubes 16 is ensured by a baffle body 18. For this purpose the
baffle body 18 is arranged in the distributor cone 8 and in the
direction flow of the cracking gas before the floor 14 and has a
form conducting the cracking gas to the passage holes 17, which
form in the present case is that of a cone with circular base area
pointing with its apex into the distributor cone 8.
In the case of a distributor cone 8 of 60.degree. to 100.degree.
angle and with a displacement body 18 causing a chamber loading in
the distributor cone 8 of 90 to 125 kg. per second and cubic metre,
especially favourable flow conditions are achieved.
The cracking gas flows through the fire tubes 16, and by contact
with the cooled tube wall of the fire tubes 16, within 15 to 20
milliseconds, loses so much heat that a temperature of 500.degree.
to 550.degree.C is reached and the chemical condition of the
cracking gas is frozen, that is to say re-formation of the cracking
gas is prevented.
The cooling of the fire tubes 16 takes place according to FIG. 2 in
a manner in which cooling medium, in this case water, is conducted
through a central, supply pipe 19 between the floors 14 and 15,
which form a closed space with the pressure jacket 13 of the
container 10. At the end facing the floor 14 the supply pipe 19 is
connected with an intermediate floor 20 which surrounds the fire
tubes 16 with guide tubes 31 with an interval adequate for the
water throughflow for their cooling.
The water flows in natural circulation upwards through the
container formed by floors 14 and 15 and the pressure jacket 13,
that is to say when the space formed by the floors 14 and 15 and
the pressure jacket 13 is filled with water, the water is warmed on
the common floor 14 and on the fire tubes 16. Thus the water
experiences a corresponding upward thrust so that it flows along
the vertically arranged fire tubes 16 through the guide tubes 31
and continuously cools the tubes 16. Since the water is introduced
in the boiling condition, the heating of the water on the common
floor 14 and the fire tubes 16 leads to steam formation. As a
result of the steam formation the water takes up very large
quantities of heat on the fire tubes 16 and the floor 14. Moreover
the steam formation reinforces the flow on the fire tubes 16, in
contrast to the known cooling devices.
Particularly favourable cooling conditions are present on the floor
14 if with adequate base area of the distributor cone 8 the ratio
of the heat emitting surface to the heat absorbing surface is
greater than 2. The heat emitting surface is the surface of the
floor 14 charged with cooling medium, while the heat absorbing
surface is the surface of the floor 14 charged with cracking
gas.
The guide tubes 31 together with the intermediate floor 20 at the
same time act as dirt pockets in which scale and the like
impurities can collect. This prevents these impurities from
settling in thermally insulating manner on the floor 14 to be
cooled and deteriorating the heat transmission between floor 14 and
cooling medium.
The cooling medium rising as a water-steam mixture is fed through
overflow pipes 32, which are connected in the direction of flow of
the cracking gas directly upstream of the floor 15 to corresponding
openings in the pressure jacket 13, to a known evaporation drum 51,
while at the same time boiling water fills up from the evaporation
drum through the supply pipe 19.
For the maintenance and cleaning of the space formed by the floors
14 and 15 in the pressure jacket 13 a washing and drainage outlet
33 is fitted to the pressure jacket 13 between the floor 14 and the
intermediate floor 20, which outlet consists of a pipe and a
shut-off slide valve or cock (not shown).
The cooled cracking gas issuing from the heat exchanger 1 at
360.degree. to 450.degree.C flows into a gas collector hood 34
flanged to the pressure jacket 13 and converging in the direction
of flow of the cracking gas, which hood continues in a conduit 35.
The conduit 35 opens with the conduits 35 of the other three heat
exchangers 1 into a collector device 36 which is assembled
similarly to the distributor device 3 and recombines the cracking
gas current previously divided by the distributor device 3, in
order to feed it to a further cooler section or to a processing
apparatus.
In a further example of the heat exchangers shown in FIG. 4,
between the lower floor 40 and the upper floor 41, fire tubes are
welded in as partially double tubes, namely with an inner tube 42
and an outer tube 43. In this case the fire tubes are formed as
double tubes especially in the upper part and over two-thirds of
their length.
At the point where the fire tubes merge into double tubes, the
inner tubes 42 and the outer tubes 43 are tightly connected with
one another, for example by welding, with a common transition part
44. While the fire tubes then are connected in the same way as
according to FIGS. 1 to 3 with the lower floor 40, which is
upstream in the direction of flow of the cracking gas, the fire
tubes are tightly connected at their other ends only at by outer
tube 43 to the upper floor 41. The inner tubes 42 of the fire tubes
are conducted out through the upper floor 41 and are tightly
connected with a corresponding flange or floor 45 of the gas
collector hood, which is not further illustrated in this case.
Since the pressure jacket 46 and forming with the floors 40 and 41
a container for the cooling medium, is not connected with the floor
45 but terminates with the floor 41, thus atmospheric air can
penetrate into the cavity between the inner tube 42 and the outer
tube 43. This formation of the fire tubes, with the same operation
as in the heat exchangers 1 according to FIGS. 1 to 3, has the
advantageous consequence that by reducing the passage of heat the
temperature on the inner wall of the fire tubes, especially in
their upper region, always lies above the maximum condensation
point of the cracking gas, although the temperature on the outer
wall of the outer tube 43 lies substantially below the temperature
pertaining to the maximum condensation point.
The heat exchanger according to FIG. 4 differs otherwise from the
heat exchangers 1 according to FIGS. 1 to 3, apart from in the fire
tubes, essentially only by the supply of the cooling medium, that
is to say in the formation of the supply pipe. According to FIG. 4
the descending pipe 47, consists of a short pipe piece which, with
similar intermediate floor 20 and guide tubes 31, is provided with
an additional floor 48 at the end remote from the floor 40. With an
entry opening 49 for the cooling medium arranged adjacent to the
floor 41 in the pressure jacket 46 and with an exit opening 50
arranged in the direction of flow of the cracking gas immediately
upstream of the entry opening 49 in the pressure jacket 46, the
additional floor 48 serves to separate the heated cooling medium
from the inflowing cooling medium and thus to prevent intermixing
of the two media.
In FIG. 7, similarly to FIG. 4, a fire tube formed as double tube
is shown. In distinction from the double tube according to FIG. 4,
in the case of this double tube the inner tube 42 is pushed into
the outer tube 43 and rolled thereto at its lower end to such
extent that at this point it is firmly and at the same time
sealingly connected with the outer tube 43.
Furthermore in this example, similarly to the case of the heat
exchangers 1 according to FIGS. 1 to 3, the gas collector hood 34
is tightly connected with the container 10, while the inner tube
42, with outer tube 43 firmly and sealingly welded with the upper
floor 15, extends out beyond the upper floor 15 and is displaceably
mounted in a further floor 53 which is arranged above the upper
floor in the gas collector hood 34. The displaceable mounting of
the inner tube 42 in the further floor 53 serves for the
compensation of its thermal expansion, while the floor 53 in turn
serves to protect a sealing composition, which fills out the
interspace between the floors 53 and 15 and in doing so encloses
the inner tube 42, against the inflow of the cracking gas.
According to FIGS. 8 and 9, three cracking gas pipes 60, 61 and 62
of the pyrolysis furnace 24 open into three cooler sections 63, 64
and 65 each of which consists of four parallel-connected heat
exchangers 66 slightly inclined towards the cracking gas flow, so
that to each cracking gas pipe 60, 61, 62 there is allocated a heat
exchanger 66. The heat exchangers 66 in turn all open into a gas
collector 67 which feeds cracking gas issuing from the heat
exchangers 66 and cooled to 450.degree.C to a subsequently placed
heat exchanger 68. One common cooling water circulation 70
represented in dot-and-dash lines is provided for all the heat
exchangers 66 and 68.
According to FIG. 10 the heat exchangers 66 and the heat exchanger
68, constructed analogously with the heat exchanger 1, consist each
of a number of fire tubes 75 arranged in annular form around a
central supply pipe 71 and provided with a triple jacket 72, 73,
74, and of two cylindrical housing chambers 76 and 77.
Of the housing chambers 76 and 77, the housing chamber 77 is
situated at the upstream end, in the direction of flow of the
cracking gas, of each heat exchanger 66 and 68. The housing chamber
77 has two end walls, of which the rear wall encloses the tubes 74
of the fire tube jacketing and the supply pipe 71 as a common floor
78, while the forward end wall 79 has the same function as the
floor 14 of the heat exchanger 1.
The housing chamber 76 is situated at the rear end of the heat
exchangers 66 and 68 and is further divided by an intermediate wall
80 into a forward chamber 90 and a rear chamber 91. In this case
the tubes 74 of the fire tube jacketing open into the forward
chamber 90 and the descending pipe 71 opens into the rear chamber
91, while the tubes 73 are conducted through the rear chamber 91.
Thus in the case of an adequate seal between the tubes 73, 74 and
71 and the wall of the housing chamber 76, water can flow from the
chamber 91 by way of the supply pipe 71 to the housing chamber 77
and from the housing chamber 77 through the cavity between the
tubes 73 and 74 to the housing chamber 90.
This water flow occurs, with a suitable water supply 92 to the
chamber 91 and a corresponding water outlet 93 at the chamber 90,
when the tubes 73 are warmed by throughflowing fresh cracking gas.
Then steam forms on the hot tubes 73, which causes a strong water
flow even in the case of an inclination of the heat exchanger of
only a few degrees, for example 3.degree.. Thus the end wall 79,
similar to the floor 14, and the fire tubes 75 are adequately
cooled as in the heat exchanger 1.
At the same time however the tubes 12, in the region of the housing
chamber 76, that is to say in the region of the cooling water
entering the heat exchanger 66 or 68, with the tubes 72 prevent
condensation of the cracking gas on the fire tube inner wall, in
that analogously with the FIG. 7 example they correspondingly
reduce the thermal conductivity of the fire tubes 7 in the region
of the housing chamber 76.
Otherwise the heat exchangers 66 and 68 differ from the heat
exchanger 1 only in that the intermediate space between the gas
distributor cone and the bellows is partially filled with a sealing
composition. A leakage conduit 84 is connected to the remaining
free part of the interspace between the gas distributor cone and
the bellows. Steam can be injected additionally through the leakage
conduit 84, preventing escape of cracking gas at the point of
contact, additionally sealed by a packing ring 85, between the gas
distributor cone and the end wall 79 if the packing ring 85 should
be damaged.
The water drainage and washing outlet, designated in this case by
86, is expediently situated at the lowermost point of the housing
chamber 77.
Likewise the tie-rods or constant suspensions necessary for the
swinging and expansion-compensating mounting of the heat exchangers
66 and 68 are secured with the aid of straps and supports to the
heat exchangers 66 and 68 in such a way that each heat exchanger 66
or 68 is suspended at two points.
In assembly the heat exchangers 66 are connected with one another
in the individual cooling sections 63, 64 and 65 through lugs 94
and bolts 95 which are removed after assembly.
* * * * *