Note: Descriptions are shown in the official language in which they were submitted.
"` ~DB5~.4
The nresent invention relates to heat exchangers used,
for example, for cooling the wall and the refractory of a
blast furnace, and more narticularly to cooling boxes
(intended to be incorporated in the refractory) and
cooling plates (for ~lacing between the refractory and
the metal casing).
One aim of the invention is to provide a heat
exchanger which uses only a small quantity of cooling
liquid er unit of time.
Another aim of the invention is to provide a heat
exchanger in which a cooling liquid removes, from the
surroundings, a large ~uantity of heat per uni-t time.
Another aim of the invention is to ~rovide a heater
exchan~er in which nressure losses during circulation
of coolinq li~uid are low.
Another aim of the invention is to nrovide a heat
exchange device which only needs for its manufacture a
small ~uantity o~ material, so that, even if recourse is
had to an expensive material, such as cop~er, the cost
of the device remains low.
Finally another aim of the inven-tion is to obtain
a high coolant sneed on the ~arts to be the most intense-
ly cooled, thus makinq the heat exchange at these parts
hi~h~
In a first asnect of the invention, there is provid-
ed a heat exchanger comprising a body shaped substantial-
ly as a body of revolution and hàving first and second
end walls and a curved wall extending therebetween, the
first end wall and the curved wall being heat-transfer
1 ~ 6~ 4
walls and at least the curved wall having a substantially
smooth inner surface, a heat-transfer fluid supply ~ort
adjacent to the first end wall and ada~ted for tangential-
ly supplying heat--transfer fluid into the body, a heat-
transfer ~luid discharge port adjacent to the ~eriphery
of the second end wall and adapted for tangentially
discharging the heat-transfer fluid from the body,
whereby in use, tanqentially sup~lie~ heat-transfer fluid
flows from the sup~ly ~ort outwardly and with a rotation-
al motion about the axis of the body over the inner
surface of the first end wall and thence, with a free
helical motion around the axis of the body, over the
inner surface of the curved wall to the discharge ~ort.
With the arranqement, in use, the heat-transfer
fluid strikes the inner face o~ the first end wall of
the body, which is situated, for exampIe, in a hot ~art
o a blast furnace, at high s~eed and cooling there
takes place with ~reat e~ficiency.
Furthermore, it is ensured that the whole of the
inner surface of the first end wall of the body is
bathed by the heat-exchange fluid and that this fluid,
once set in motion in helical rotation, is brought to
the other end of the body while bathing the whole of
the curved wall.
Finally, because of the even helical movement
im~arted to the heat-exchange gluid, it is ensured that
the liquid bathes the walls of the enclosure continuous-
ly and without any swirling movement and that thereby
~B~
the cooling efficiency obtained is high.
It is preferable that, the heat-transfer fluid
flows with a rotational speed com~onent which is about
ten times greater, at the discharge ~ort, than an axial
component directed towards the second end wall of the
body.
Advantageously, deflecting members are provided for
deflecting the heat transfer fluid supplied by the supply
port to flow outwardly and with said rotational motion.
Conveniently, the fluid deflecting members comprise
curved vanes on the inner surface of the first end wall.
According to another aspect of the invention, there
is provided a heat exchanger com~rising a body shaped
substantially as a body of revoLution and having first
and second end walls and u curved wall extending there-
between, the first end wall being a heat transfer wall,
a supply port and a discharge port for heat transfer fluid,
the ports being spaced apart radially, the su~ply port
being adapted for tangentially supplying the heat transfer
fluid into the body and the discharge ~ort being adapted
for tangentially discharging the heat-transfer for fluid
from the body so that, in use, the fluid flows between
the ports in a spiral path over the inner surface of the
first end wall, the body having no internal obstacle to
such flow.
It is advantageous for the supply port and the
discharge port to be respectively adjacent the periphery
and the centre of the first end wall.
t ~ ~
Some particular arrangements may be applicable to
these cooling devices so as to make them suitable for
special ap~lications.
For this, in a first embodiment, it is envisaged
that, with the means for tangential injection of the
liquid opening tangentially into the enclosure at the
periphery or in the vicinity of the periphery thereof
and with the means for tangential discharge of liquid
situated in the center of the enclosure, the tangential
lo discharge means comprise at least one assembly of
deflecting means situated in the center of the enclosure
and a duct opening into a face of the enclosure o~osite
said deflecting means.
Because o the presence of the deElecting means,
recovery of the cooling liquid :is facilitated in its
sprial rotating movement and i-ts delivery at the port
of the discharge duct. This recovery is efec-ted more
rapidly, which further improves the flow of the liquid
and allows more efficient cooling of the walls of the
enclosure to be achieved.
The discharge duct may extend radially from the
center of the enclosure towards the periQhery of the
enclosure.
So as not to increase the thickness of the heat
exchange device, it is advantageous for the radial dis-
charge duct to be inside the enclosure, for it to extend
substantially at the same distance from the two lateral
walls of the enclosure and for it to be provided with
two assemblies of deflecting means sltuated on each side
of said duct. Preferably, the radial discharge duct is
then shaped outwardly so as to offer minimum resistance
to the liquid rotating in the enclosure.
Advantageously, the radial discharge duct opens
into a transit chamber, outside the enclosure and compris-
ing a water outlet orifice.
Another arrangement, to which recourse is had either
in combination with one or other of the preceding ones,
or in combination with the improvements of the parent
patent, consists in the tangential discharge means
comprising a duct opening tangentially into the enclosure,
at the periphery thereof, the port of said duct being
diametrically opposite the port of the tangential injec-
tion means.
In another embodiment of the invention, it is envis-
aged that, with the tangential injection means opening
into the central part of the enclosure and with the
tangential discharge means situated at the periphery
of the enclosure, the tangential injection means comprise
at least one liquid supply duct opening into at least
one face of the enclosure and subs-tantially in the center
of said face and at least one assembly of deflecting
means situated opposite the port of said duct, so as to
impart a tangential force component to the liquid
emerging into the enclosure.
The flat cooling boxes used up to now have a general
flattened substantially parallepipedic shape whose rear
~ 1 6~
part is nrovided with means for fixing to the plating and
whose front part (or nose) is Eormed by a flat face which
is fitted with a small radius to the lateral Eaces.
So as to cause the cooling liquid to flow in the
nose, there is provided inside the enclosure thus formed
at least one separating wall forcing the liquid to follow
the outer wall of the box.
However, in the 90 bends, the speed of the streams
of liquid-which are situated outermost (i.e. in contact
with the wall of the box)- is greatly reduced ; the result
is that this bend zone is poorly cooled whereas the nose
is precisely the part of the box which is the most exposed
to the heat.
Furthermore, this reduction in the speed of the
liquid may be such that recirculation, or dead water zone,
is created in the bend promoting decantation of solid
particles which slow down the heat exchange. The wall of
the enclosure heats up, which further increases scaling,
which slows down even ~urther the heat exchanges.
This cum~atlve phenomenon spreads by degrees and
the box ~inishes by being destroyed under the action of
thermo-mechanical abrasion, for poorly cooled copper
(from which these boxes are generally made) loses all
its mechanical characteristics and is very easily worn,
not onl~ by the charges but also by hot gases, dust
charqes, etc.
As far as the streams of liquid which are situated
innermost in the bend (in contact with the internal
~ 1 6~
separating wall) are concerned, their speed is greatly
increased, which may lead to very high speeds of the
liquid if the flow has been increased to improve cooling
of the plate.
The effects of this high flow rate of the liquid
are even more harmful than in the preceding case for,
in this region where the liquid undergoes a 180 change
of path, there occurs cavitation causing a pressure drop
and rapid wear of the separating wall.
lo Furthermore, the increase in the speed of the cooling
liquid can only be obtained nractically by reducing the
section of the ducts, which leads to a reduction of the
volume of liquid and so of the thermal flywheel.
Finally, these boxes are difficult to construct and
so costly.
Implementation of the arrangements in accordance
with the invention for constructin~ a flat cooling box
allows an enclosure to be obtained which comprises no
` bend having a small radius of curvature and in which the
streams of liquid follow paths whose radii are suffi-
ciently ~reat to avoid creation of the above-mentioned
dead zones , furthermore, there exists no nart likely
to cause a cavitation phenomenon. Deposits of solid
narticles are then avoided and no region of the box is
subjected to particular destructive wear.
~oreover, it will 'oe noted that the whole of the
cooling liquid mass is set in rotation inside the
enclosure and that the whole of this mass participates
1 1 ~51 ~ ~
at all times in cooling the walls. The result is a
considerably increased cooling efficiency with respect to
what was obtained up to now.
Finally, the manufacture of flat boxes thus construct-
ed is very simple and so less espensive than that of knownflat boxes.
In a preferred embodiment, there is provided, for
supply and discharge of the cooling liquid, connection
means dis~osed side by side and connected to the enclosure
by ducts which extend between two planes containing the
two substantially parallel faces of the enclosure.
Finally, a complementary arrangement, more particular-
ly advantageous in the case where the heat exchange device
ls intended to be used as a cooling box, consists in
providing a second enclosure covering at least the front
part of the first enclosure, no communication for the
booling liquid existing betwees~ the first and second
enclosures.
The addition of this second enclosure increases
considerably the efficiency of the heat exchange device
of the invention for a bulk which is in general scarcely
greater.
Moreover, by causing the cooling liquid to flow in
opposite directions in the two enclosures, better
distributed and more even cooling is obtained over the
whole of the periphery of the device since there
corresponds, to one region of an enclosure through
which flows heated liquid, a region of the other
3 3 ~
enclosure through which still cold liquid flows.
The arrangements of the invention find a second
application in the so-called "vaporization" oooling
boxes in which there is formed vapor bubbles on contact
with hot walls.
This type of box is arranged so that the vapor
bubbles are collected, by gravity, in the discharge
duct for the cooling liquid.
The major disadvantage of the vaporization boxes
used at present is that the heat is removed essentially
by convection. In the case of harsh heat aggression in a
given zone of the box, this heat flow may be all the less
efficiently removed since in general no pump is provided
in the circuit and since the flow of the cooling liquid
takes place naturally by a thermosiphon phenomenon. The
result is a calefaction phenomenon in the zone considered,
causing in the ducts formation of a vapor plug which
interrupts, and may even sometimes reverse, the natural
flow of the cooling liquid. Uncooled, the box is rapidly
destroyed.
On the contrary, in a cooling box constructed in
accordance with the invention, the vapor bubbles are
subjected to the action of the contrifugal force due to
the rotation of the liquid mass. Thus, because of the
existence of this gravitational field, the vapor bubbles
are torn from the wall as fast as they are created and
are carried towards the center oE the box.
For a cooling box formed in accordance with the
~ ~ 6~1 1 4
preceding arrangement, it is provided for the radial duct,
extending from the central zone of the box to the rear
thereof, to be situated in the upper part of the box (in
- the mounted position thereof), and preferably outside the
enclosure, so as to form a chamber for recovering the
water-vapor emulsion which is then discharged.
The arrangements of the invention find a third appli-
cation in cooling plates.
The cooling plates used at present are in the form
of rectangular metal plates through which pass a vlurality
of ducts intended for circulation of the cooling liquid.
The ducts are independent of each other and each has an
inlet port and an outlet port provided respectively with
securing, means for connection to outside hydraulic
circuits. Furthermore, these plates comprise securing
means for the fixing thereof to the plating of the blast
furnace.
Tyr~ically, a known coolinq plate comprises at least
twelve securing points, either for fixin~ them or for
connecting them to outside circuits.
The very high temperatures to which the plates are
exposed cause expansions which are incompatible with
such a hi~h number of rigid ~oints and the plates are
subjected to mechanical stresses such that they are
rapidly made unusable.
Furthermore, the cooling liquid flow rate in these
known plates is too low and the thermal fly-wheel thus
created is too small to provide efficient coolinq of
1 1 4
the plating.
On the contrary, by its very design, the cooling
device of the invention, because of the relatively high
volume of liquid set in ro-tation, has a high thermal
fly-wheel which allows much better cooling than that
obtained up to present.
As for the problem of mechanical stresses, it is
resolved in the cooling device of the invention by the
fact that :
- the two pipes for supplying and discharging the
cooling liquid extend approximately perpendicularly to
that one of the walls of the device which, in the mounted
position in the blast furnace, is in contact with the
platinq of said blast furnace, from the central region
of said wall,
- the two ducts are concentric, at least in the
vicinity o:E said wall,
- and the means for fixing -the plate tu the ~lating
of the furnace comprise that one of said ducts which is
outside the other and an orifice, pierced in the plating,
adapted to receive said ou-ter duc-t, securing means being
used for securing this outer duct to the edge of the
orifice or to the zone of the plating surrounding the
orifice.
Thus, with these arrangements, the cooling plate
is only secured to the ~lating in a single zone, which
removes any problem of mechanical stresses due to
expansion during operation.
11
~16~14
~oreover, still because of the simple structure of
the cooling devices in accordance with the invention,
cooling plates thus formed are simple to manufacture,
so less expensive, than the plates known at present.
A variation of the plate which has just been
described consists in providing it with an axial cavity
open at both ends, the enclosure surrounding the cavity
and the supply and discharge ducts surrounding at least
partially the cavity, the transverse dimensions of the
cavity being sufficient for it to be possible to introduce
therein an elongate and cylindrical cooling device.
It may thus be seen that a combined coollng device,
associating a cooling plate and a cooling box, which
ensures a particularly favorable result since, for a
bulk which is that of the cooling plate, deep cooling
is effected within the refractory material, on the one
hand, and a thermal screen is Eormed protecting the
~lating, on the other.
Enbodiments of the invention will now be described
by way of example. In this descri~tion, reference is made
to the accompanying drawings in which :
~ig. 1 shows schematically in section a cooling
box in the wall of a blast furnace ;
Fig. 2 is a section along line II-II of Fig. 1 ;
Fig. 3 is a section similar to Fig. 2 of a second
cooling box ,
Figs. 4 and 5 are resectivelv a longitudinal and
a cross section of a third cooling box ;
12
Fig~ 6 is a vertical sectional view of a coolin~
plate ;
FigO 7 is a section along line VII-VII of Fig. 6 and
shows also a portion of a blast furnace ;
Fig. 8 represents schematically one embodiment of a
heat exchange device constructed in accordance with the
invention ;
Fig. 9 is a sectional view along line VIII-VIII of
Fig. 8 ,
Fig. 10 represents schematically another embodiment
of a heat exchange device in accordance with the invention;
Fig. 11 shows schematically yet another embodiment
of a heat exchange device in accordance with the invention;
Fig. 12 shows schematically yet another embodiment
of a heat exchange device in accordance with the invention;
Fig. 13 is a side sectional view of a cooling plate
constructed in accordance with the invention ;
Fig. 14 is a sectional view along line XIV-XIV of
the cooling plate of Fig. 13 ,
Fig. 15 shows a further variation of the cooling
plate of Figs. 13 and 14 ; and
Figs. 16 and 17 show respectively two possible
arrangements of cooling plates and boxes in accordance
with the invention.
Although it may be used in very different fields,
a heat exchanger of the invention finds particularly
advantageous applications in the field of iron and steel
metallurgy and more particularly in blast furnaces in
13
1 4
which it is necessary to cool efficien-tly in particular,
on the one hand, the steel plating surrounding on the
outside the refractory lining and, on the other hand,
the re'fractory lining itself.
Fig.-1 shows a cooling box 1 and the plating 2 of
a blast furnace.
As shown in Fig. 1, cooling box 1 is in the form of
an elongate tubular element of revolution.
It passes through the plating 2 of the blast furnace
through an opening 3 formed therein and is disposed so
that its axis of revolution 4 is substantially horizontal.
Over the qreatest part of its length, it is thus surround-
ed by the refractory 5, a nose 6, or end of the box turned
towards the inside oE the blast furnace and so towards
the heat source, being also located in the refractory 5
or on the contrary disengaged, denending on the wear of
the refractory 5.
sox 1 is ~ormed from a good heat conducting material
and is capable oE withstanding without damage the heat
and mechanical stresses ; for this purpose, steel, cast
iron or copper or an alloy with a high copper content
is used. Furthermore, box 1 is fixed to the plating in
an appropriate way, for example by welding with or
wi-thout ~acking material depending on the nature of
the material used for constructing the box.
Box 1 is formed by a closed jacket 7 which comDrises:
- a cylindrical sidewall 8, as shown in Fig. 1, or
slightly in the form of a truncated cone with its conicity
14
~ 1 B~
directed towards nose 6 (for facilitating the positioning
or removal of the box through hole 3 in plating 2) ;
- an outer end wall 9 situated at the end of the
box outside plating 2, this wall being flat ; and
- an inner end wall 10 situated at the nose end of
box 1 which may be flat (as shown in Fig. 1) or bulging.
This jacket 7 defines a closed enclosure 11 in which
a cooling liquid is set in motion as will be described
further on.
The inner surface 12 of sidewall 8 presents no
roughness and is substantially smooth so as to create no
turbulence in the liquid in motion.
In box 1 there is provided an orifice 13 Eor inject-
ing cooling liquid and an orifice 1~ for discharging this
liquid, these two orifices being located respectively at
the two axially oDposed ends of the box.
As nose 6 oE box 1 forms the part thereof situated
the closest to the heat source, it is very desirable
that the cooling liquid be injected at this point. For
this purpose, an inlet pipe 15 is provided which sealing-
ly passes through the outer wall 9 of box 1 and whose
orifice 13 is located immediately proximate the inner
surface of the inner wall 10. For a purpose which will
become clear later, ~ipe 15 is straight and its axis
merges with the axis of revolution of jacket 7.
~ith this arrangement discharge port 14 is situated
adjacen-t the outer end wall 9.
So as to be sure that the cooling liquid licks
~ ~S~l~
continuously the inner surfaces of the walls of jacket 7,
more particularly surface 12 of sidewall 8, it is provided
that the mass of cooling liquid be actuated with a rota-
tional movement about the axis of revolution 4 of jacket 7.
So as no-t to complicate the manufacture and the
maintenance of the device, this setting in rotation of
the liquid mass is obtained in a simple way by injecting
the liquid through port 13 wi.th a tangential speed
component.
In this connection, it should be noted that nose 6 is
the part of the cooling box whixh is the most exposed to
the heat ; it is then through nose 6 that maximum cooling
must be effected. It is then important for the cooling
liqui.d leaving port 13 not only to strike (arrows 60 of
Fig. 1) the inner wall 10 of nose 6, in the central
region thereof, ~ipe 15 being axial, but also, from this
moment on, to be deflected with a rotational speed compon-
ent tarrows 61 and 64 in Figs. 1 and 2) so that it ~athes
the whole of the inner wall 10 of nose 6 : thereby, the
whole of nose 6 of box 1 partici ates in the cooling.
In addition, the cooling liquid must be brought back
to the outer wall 9 and dischar~e ~ort 14 while effecting
a helical mGvement (arrows 62 in Fig. 1) along the inner
surface 12 of sidewall 8. Thus, the liquid in motion must
present two speed com~onents :
- an axial component (arrow 63 in Fig. 1) directed
towards the outer end wall 9 and intended to cause the
liquid to return to the outer end of the box~
16
1 :1 6~ 4
- and a rotational componerlt (arrows 61 and 64 in
Fi~. 2) intended to make the liquid turn along wall 8 so
as to cool this latter.
of course, the above explanation of the beakdown
of the movements executed by the mass of liquid leaving
port 13 is theoretical and, in practice, these movements
are intercombined (arrows 62 in ~ig. 1). To this end, it
is provided that the inner surface 16 of the inner end
wall 10 is formed to have hollows or projections 17
constituting blades in the form of s~iral sections dispos-
ed all around port 13 and acting as deflectors for the
liquid ~rojected by port 13 situated axially opposite,
so as to communicate thereto a rotational component.
Thus, from injection port 13, the stream of liquid
strikes the inner face of nose 6 and, from this moment on,
is deflected by the inner end wall 10 at the same time as
it is rotationnaly deflected by blades 17 (arrows 61 and
64).
So that the rotational movement of the liquid mass
takes place evenly and without turbulence, it is further-
more desirable for the discharge of the liquid through
port 14, at the opposite end of box 1, to take place
tangentially and for a discharge ~ipe 18 to be suitable
dis~osed in relation to wall 8 of jacket 7. Due to the
fact that the inner surface 12 of wall 8 of jacket 7 is
smooth and that the inlet ~i~e 15 is coaxial to the axis
of revolution 4 of jacket 7, it is certain that, under
the action of the tangential speed component of the
17
1 ~ 6Sl 1 ~
liquid injected through port 13, the mass of liquid is
propelled with an undisturbed rotational movement and
that the liquid flows smoothly from the inner end wall
10 towards the outer part of the box while continuously
licking the wall 8 o~ jacket 7.
In the cooling box 65 of Fig. 3, an inlet pipe 66
bringing cooling liquid has a diameter a little greater
than that of pipe l5 of the box of Figs. 1 and 2.
In box 65, the deflector means are formed by two
projecting walls, respectively 67 and 68, forming respect-
ively arcs of two spirals wound one in the other. Similar-
ly, in the preceding examnle, these two projecting walls
are carried by an internal face of a nose of the cooling
box 65.
As shown in Fig. 3, wall 67 comprises a central part
69, i.e. located in a zone of low radius of curvature of
the spiral, disposed across a supply port 70 of the inlet
pipe 66 , this central part 69 presents two regions, of
substantially equivalent lengths, having opposite curva-
tures, i.e. the central part 69 has the general shape of
an S.
Beyond the central part 69 (towards the left in Fig.
3), the projecting wall 67 develops along a spiral, with
a continuously increasing radius of curvature, substan-
tially over a complete turn. At this point, it joinsagain at 71 a side wall 72 of the box 65.
As for the other projecting wall 68, it is initiated
substantially on the radius joining the axis o~ revolution
18
~ ~ ~5 1 ~ ~
of the box 65 to zone 71 along the side wall 72 of the
box 65, and cancels out disturbances sustained by streams
of liquid at the point of their change of guiding surface,
i.e. from the internal face of the nose of the box 65 to
the in-ternal face of the side wall 72.
When the cooling liquid leaves the supply port 70
of the inlet pipe 66, it is divided into two streams by
the S-shaped region 69. A first part of the liquid is
rotated following arrow 74 and flows along the wall 67,
then between the wall 68 and the o~lter wall 72 of the
box 65. A second part of the liquid is rotated following
arrow 75 and flows first between the walls 67 and 68,
then between the walls 67 and 72.
Because of the lengths of the walls 67 and 68 are
appreciably greater than those of blades 17 of the
coolinq box of Figs~ 1 and 2, t:he liquid can be more
evently set in rotation, the liquid being guided for a
longer period of time.
In order to improve the effect obtained, S-shaped
region 69 of wall 67 can be made to penetrate a little
inside tne inlet pipe 66, thus the liquid is di~7ided
into two streams and its rotation may be initiated a
little before it leaves through the supply port 70.
Of course, the deflector means may just as well be
carried by the end of the inlet pipe 66 which is situa-ted
around the supply port 70.
Furthermore, so as to extend the guiding of the
streams of liquid, the walls 67 and 68 may be extended
19
~ ~ 6 ~
for a short distance.
Figs. 4 and 5 show a coolinq box 80 in which a part
of the deflector means is carried by the end of a liquid
inle~ pipe 82 (creating a primary rotation) whereas another
part of the deflector means is carried by an internal face
86 of a nose 87 of the cooling box 80 (and completes the
setting of the liquid in rotation).
As shown in Figs. 4 and 5, the cooling box 80, which
may be formed as a whole like the box 1 of Fig. 1 is
provided with an annular jacket 81 surrounding the liquid
inlet ~ipe 82, and defining with an outer wall 83 of the
box 80 an annular chamber 84 in which the cooling liquid
is intended to flow helically in the Eorm of a relatively
thin layer and at high speed.
Towards its outlet 82a, the liquid inlet pipe 82 is
provided with a deflector 85 partially engaged in the
pipe 82 and disposed end to end with the internal face
86 of the nose 87 of the box 80.
A deflecting member 85, in cross-section, is in the
form of a four-legged cross-piece, each leg 88 being
axially curved so as to form a deflecting trough 89.
Deflecting member 85 is an insert in the end of
pipe 82.
Moreover, the internal face 86 of nose 87 of box 80
is not flat, but is substantially in the shape of a
truncated cone with a central ~art in the shape of a
spherical skull-cap, the whole forming a prominence
directed inwardly of box 80. Furthermore, this internal
~ 3 B~
face 86 carries deflecting walls 90, 91, 92, 93 in the
shape of arcs of a spiral, projecting parallel to the axis
of revolution of the enclosure.
The first wall 90 is situated opposite one of the
deflecting troughs 89 of deflecting member 85 and develops,
with a curvature identical at the start to that of the
trough, along an arc of a s~iral for approximately a
complete turn, the radius of curvature increasing conti-
nuously.
The second wall 91 starts substantially at the free
end of the first wall 90, while being located inwardly of
the spiral described by wall 90 at a distance e thereErom.
Furthermore, walls 90 and 91 face each other over a
curvilinear length 1. ~all 91 clevelops in its turn along
an arc of a spiral approximately over a quarter of a turn.
The third wall 92, beginni.ng at a distance e from
wall 91 and situated opposite t:hereto over a length 1,
develc~ps along an ars of a spiral approximately for a
quarter of a turn~
Finally, the fourth wall 93, situated at distance e
from wall 92 and also from wall 90, extends over an arc
of a spiral for approximately a quarter of a turn parallel
to wall 90.
In addition, as can be best seen in Fig. 4, the free
edges of the deflecting walls 90 to 93 are coplanar and
the front end of annular jacket 81, which is also flat,
is disposed end to end against the free edges of deflect-
ing walls 90 to 93. Thus, there is defined an assembly
21
of spiral passages of variable and increasing widths
(taken in the directlon of flow of the liquid) intercommu-
nicating through necks of lengths 1 and widths e.
With this arrangement, the cooling liquid brought
by pipe 82 begins to be set in rotation by the deflecting
member 85 with troughs 89 before it leaves through outlet
82a of pipe 82. At thls moment, the rotational movement
continues to be communicated to the liquid by deflecting
walls 90 to 93.
Because of the relative positions of walls 90 to 93,
the liquid is caused to pass through a neck of width e,
irrespective of the ~ath followed. Because of the rela-tive
narrowness of these necks, the liquid is accelerated
during its passage therethrough, which ensures that the
cooling liquid will begin to follow a helical path, in
annular chamber 8~, with a rotational speed component
sufficien-tly high for it to reach the o-ther end of the
cooling box at a tangential speed which allows discharge
thereof by simple inertia. Experiments have shown that,
in order to obtain this result, it is advisable for the
rotational component to be about ten times greater than
the axial component directed towards the outer end of
box 80.
By way of modification, a one ~iece independent part
may be formed obtained for example by moulding, compris-
ing deflecting member 85 and deflecting walls 90 to 93,
this independent part being fitted into the end of pipe
82 and disposed end to end against the internal face 86
22
1 1 4
of nose 87 of coollng box 80.
The deflecting member 85 may also be formed by
moulding to form a single piece with nose 87 of coollng
box 18 and wlth deflectlng walls 90 to 93; under these
conditions, member 85 flts lnto the end of pipe 82 when
this latter is positioned in box 80 and contrlbutes to
facllitatlng this posltlonlng.
Referring to Figs. 6 and 7, there will now be des-
cribed another embodlment of the invention.
Here a cooling box has a flattened shape and in the
art is called a "cooling plate". This terminology will be
adopted in the continuation of the description.
Such plates are not disposed in the refractory like
the elongate boxes previously described but between the
refractory and the internal face of the plating so as to
form a continuous or discontinuous thermal screen,
depending on the gap left between two consecutive plates,
between the heat source and the plating.
These plates are, like the elongate boxes, made from
a heat conducting and mechanlcally resistant material,
such as steel, cast iron or co~per.
Referring to Figs. 6 and 7 in which is shown a plate
20, this plate 20 has a flattened shae, its parallel
faces 21 and 22 being respectively in contact wlth
~lating 23 and the refractory 24 of a blast furnace, and
it ls hollow to allow cooling to flow.
Faces 21 and 22 are round. An injec-tlon port 25
opens into plate 20 tangentially to a substantlally
23
cylindrical sidewall 26.
A discharge port 27 ooens tangentially adjacent the
center of plate 20 and a discharge pipe 28 coils towards
the center of the plate and is bent so as to leave the
plate through the face 21 in the center thereof. Liquid
inlet 25a and dischar~e 27a pi~es are disposed substan-
tially perpendicularly to the plate.
Plate 20 has the general aspect of a snail shell.
It will be noted that the axes of the injection 25
lo and discharge 27 ports are respectively at distances R
and r from the center C of box 20. For this reason, so
that the inlet and outlet flows of liquid may be equal,
it is necessary for section S of the dischar~e oort to
be ~reater than section 5 of the in~ection port.
The equality of flows produces as a consequence :
Vl S = V2 . S
V1 and V2 designating the inlet and outlet speeds which
are in the ratio of distances R and r, i.e. :
V1 V2
=
R r
The following geometrical condition must then be
achieved :
R _ S
r s
Similarlv, as in the case of the elongate box 1 of
Fig. 1, it is necessary for the internal walls of olate
20 to oresent no roughness so as not to create turbulence
24
~ ~6~14
within the mass of liquid in motion.
During operation, because of the tangential injection
of liquid through port 25, the liquid mass is propelled
with a rotational movement and evenly licks each point of
S walls 21, 22 of plate 20. It can be considered that the
stream of liquid, introduced through port 25, coils round
within the inner volume of the plate before reaching
discharge port 27.
With the setting in rotation of the mass of cooling
liquid, with the help of suitable deflector means, and by
disposing the injection and discharge ports for the liquid
in o~posite regions of the device, it is ensured that each
zone of walls 21, 22 to be cooled is licked by the li~uid
and is thus efficiently cooled.
By arranging for walls 21, 22 not to have any rough-
ness and for nothing to opose the rotational motion of
the liquid mass, this latter is the seat of no turbulence
and all the zones of walls 21, 22 to be cooled whichever
they are and wherever they are located, are cooled in the
same manner and with the same efficiency. Furthermore,
pressure losses in a hydraulic circuit supplyin~ plate 20
are practically eliminated.
lt is thus ~ossible to calculate very accurately the
minimum flow of liquid to be injected into plate 20 so as
to obtain a predetermined cooling and so as th achieve
substantial economies on the amount of liquid necessary
and, conse~uently, on the cost price of the cooling.
The flow of the liquid can also be accurately calcul-
~ ~6~1~4
ated so that it heats up to a high tem~erature, this
heating up going ~ossibly far enough to cause vaporization,
which allows the efficiency of the device to be further
increased due to the fact that the vapors, while escaping,
help in the movement of the remaining liquid mass.
The geometrical shaes of the component parts of
~late 20 are simplified. This reduces the amounts of mate-
rial necessary and the manufacturing cos-ts and so the
overall cost price of the device. Thus, manufacturing of
plate 20 from steel, cast iron or cop~er may be considered.
It is possible to mount several plates 20 or boxes 1,
65, 80 in series by intercoupling them ; thus there can
be provided for exam~le several intercoupled elongate
cooling boxes, coupling between a cooling box and a
cooling plate or intercoupling between several cooling
plates.
DifEerent particular embodiments of heat exchange
devices of the flat type appropriate for certain particular
applications will now be described.
Referring first of all to Figs. ~ and 9 concerning a
first embodiment, cooling box 60 comprises an enclosure
61 cylindrical in revolution having a flattened shape,
i.e. its height is small in relation to its diameter.
A duct 62 for supplying cooling liquid opens tangen-
tially into enclosure 61.
For discharging the li~uid there is provided, on the
one hand, an outlet 63, substantially diametrically oppo-
site the ~ort of suDply pi~e 2 and, on the other hand, a
26
~ :1 6 ~
channel 63 extending radially a-proximately from the
center to the periphery of enclosure 61 ; channel 63 is
situated at the same distance from flat walls 64 of the
enclosure and lt is flattened and shaped, as can be seen
S at 65 in Fig. 9, so as to only disturb the liquid flow
to a lesser degree.
Two holes 66, pierced respectively in the lateral
faces thereof and contered at the center of the enclosure,
allow the cooling liquid to pass from the enclosure into
channel 63.
To facilitate this passage, there is furthermore
provided, on each side of channels 63 (i.e. between each
face 67 of the channel and each wall 64 oE the enclosure),
a deflecting device 68 formed from blades wound in the
direction of the center of holes 66.
Channel 63 extends towards the rear of cooling plate
60, i.e. opposite the zone (or nose) 69 intended to be
directed towards the reg`ion of the blast furnace to be
cooled when the box is installed in its operating posi-
tion.
Channel 63 opens into a discharge chamber 70, conti-
guous with enclosure 61 and situated therebehind.
A duct 71 for discharging the cooling liquid opens
into chamber 70, preferably op~osite the port through
which channel 63 opens into chamber 70 or opposite port
63a.
The cooling liquid (in general water), supplied by
duct 62 (arrow 72) arrives in enclosure 61 in which,
27
~ J6St~4
considering the form thereof, there is created a spiral
movement (arrow 73). A ~art of the liquid of -the external
stream, which is in fact the most heated in contact with
the wall of nose 69, passes directly through port 63a
(arrow 73a) to be discharged. The rest of the mass of
water, once in the vicinity of the central region of the
enclosure, is recovered by the deflecting devices 68
(arrow 74) and penetrates into channel 63 from where.it
passes into chamber 70 (arrow 75) then leaves through
duct 71 (arrow 76).
It will be noted that the whole of cooling box 60
is comprised between two ~arallel planes containing the
faces 74 of the enclosure. The result is that box 60 may
be easily introduced through the plating of -the blast
furnace into its housinrJ provided in the refractory
material. Conversely, it may be easily removed therefrom,
for exam~le with a view to its replacement.
Fig. 10 (in which the elements identical to those in
Figs. 8 and 9 are designated by the same reference number)
shows a so-called "vaporization" cooling box 77 whose
construction corresnonds in a general way to that of box
60 of Figs. 8 and 9, with the excention of channel 63
which is transferred to the outside of the enclosure.
More precisely, there is associated with one of the
walls of the enclosure (in the present case the one 78
which is disposed at the to~ in the mounted ~osition of
the box on the plating of the blast furnace, such as
shown in Fig. 3), an elongate shell 79 defining with wall
28
78 an outer channel 80.
A supply duct 62 opens tangentially into enclosure
61, for example in accordance with the configuration of
Fig. 1 or in accordance with any other configuration,
whereas a discharge duct 71 leaves from channel 80. Just
as in the preceding embodiment, vanes 68 are provided
for causing the liquid to pass through a hole 66 communi-
cating enclosure 61 with channel 80.
Another hole 81 is provided for connecting discharge
chamber 70 with channel 80.
During operation, the vapor bubbles which form
particularly in contact with the wall of nose 69, the
most exposed to the heat, are torn away as fast as they
are created and carried by the rotating liquid mass into
enclosure 61.
Considering the gravitational field which reigns
within the liquid mass, the vapor bubbles are brought to
the center of enclosure 61 where they pass into channel
80. Since the liquid is in continuous circulation within
the enclosure, there cannot be formed, alont the internal
face of the walls, particularly in the nose, a vapor veil
preventing heat exchanges neither a vapor plug stopping
circulation of the water.
The cooling box 83 shown in Fig. 11 is designed,
contrary to the proceding ones, with a central inlet and
a tangential discharge.
A supply duct 84 opens into the center of an enclo-
sure 85 cylindrical in revolution, the liquid penetrating
perpendicularly to the circular face 86 of the enclosure.
29
~ 3 16$1 ~ ~
Deflecting means 87, formed for example like those 68
of Figs. 8 to 11, impart to the liquid a tangential compo-
nent so that it is set in rotation and describes a spiral
path from the inside to the outside of the enclosure
(arrow 88).
A discharge duct 89 extends tangentially and recovers
the heated liquid.
Fig. 12 shows yet another embodiment of a cooling box
in accordance with the invention. Box 90 of Fig. 12 is
designed from plate 60 of Figs. 8 and 9 all the elements
of which it employs (the same reference numbers have been
kept in Fig. 12).
There ist however added a second enclosure 91 which
is simply formed by a tubular duct bent in a semi-circle
so as to assume the rounded shape of nose 69 of plate 60
of Fig. ~. Tubular duct 91 is connected to the outside
hydraulic network by means of supply 92 and discharge 93
ducts.
It will be noted that, in enclosure 61 and in duct 91,
the flow directions for the liquid are opposite (respecti-
vely arrows 94 and 95).
The result is that in the vicinity of discharge duct93, where the liquid already heated by its travel through
duct 91 is less efficient, beneficial cooling is provided
by the cold liquid arriving through duct 62 and emerging
into enclosure 61. And conversely in the region of ducts
71 and 92. It is thus possible to obtain better distribu-
tion of the cooling of the refractory and, in a general
~ 3~114
way, improved eficiency.
It will be noted that in Fig. 12, cooling box 91 has
been shown in an operational position, i.e. as has already
been explained morever above, the plate extends practi-
cally perpendicularly to the plating 96 of the blastfurnace to which it is fixed in an appropriate way by
means of an intermedia-te shoe 97 and it penetrates into
the refractory 98, its nose 99 being -turned towards the
hot re~ions of the blast furnace.
Figs. 13 and 14 show a cooling plate lOOr for insert-
ing (as has already been indicated above) between the
plating 101 of a blast furnace and the refractory wall
(not shown).
Cooling plate 100 has an enclosure 102 cylindrical
in revolution, a supply duct 103 for the cooling liquid
and a discharge duct 104 for this liquid.
The two ducts 103 and 104 ex-tend, at least in a zone
adjacent the coolinq plate, substantially perpendicularly
to that one 105 of the walls of the enclosure which is
turned towards plating 101. Furthermore, the two ducts
103 and 104 are coaxial, duct 104 bein~ inside duct 103,
which surrounds it.
By way of example, the arrangement for the cooling
plate may be the following.
Supply duct 103 communicates with a channel 106,
provided on the outer face of said wall 105 of the
enclosure, which opens into enclosure 102 at the peri-
phery thereof through a port 107. A deflecting wall 108
31
J 1 ~
is provided in front of port 107 to deflec-t the liquid
flow so that it gushes tangentially into the enclosure.
Diametrically opposite port 107 is an outlet port
109 by means of which enclosure 102 commu'hicates with a
channel 110 (also situated outside wall 105 for example)
ending in a central chamber lll of the enclosure. This
central chamber communicates with the rest of the enclo-
sure through apertures 112. In chamber 111 are also
disposed deflecting vanes 112 situated opposite the port
through which discharge duct 104 opens into said chamber
111 .
For fixing cooling plate 100 in the blast furnace,
a hole 1l3 wlth a diameter corresponding substantially to
the outer diameter of supply duct 103 is bored in plating
101 ; duct 103 introduced into hole 113 is welded to the
plating. Cooling plate 100 is thus securely fixed to the
plating solely by its central region, represented by duct
103 serving as a fixing sleeve.
Whatever the deformations which the cooling plate
may undergo through the action of the heat, i-t will be
able to freely expand without it being the seat of des-
tructive stresses as was the case with the prior cooling
plates presenting a plurality of fixing zones.
Of course, it will be understood that the arrangements
which have just been described and combining the supply
and discharge means for the cooling liquid with the fixing
means are not dependent on the particular configuration
of -the enclosure shown in Figs. 13 and 14, and which has
32
~ ~S~4
only been given by way of example, and that they may just
as readily be associated with other enclosure configuration,
such as those previously described.
Fig. 16 shows an arrangement combining cooling plates
100, such as those which have jus~ been described, disposed
in a staggered arrangement and cooling boxes lOOa disposed
in the free sectors between the ~lates.
Thus deep coollng of the refractory, provided by the
boxes, may be combined with surface cooling, intended to
lC protect the plating, created by the plates~
Fig. 15 shows a cooling plate 114 which is a variation
of the cooling plate 100 of E`igs. 13 and 14.
Plate 114 comprises an axial annular chamb2r 115
surrounding an axial cylindrical cavity 116 open at both
its ends.
~nnular chamber 115 is subdivided into two semi-
cylindrical half ehambers 117 and 118 in whieh emerge
respeetively the supply 119 and diseharge 120 duets for
the eooling liquid.
For the rest, the eooling plate may be arranged in
a substantially identical way to plate 100 of Figs. 13
and 14 or be construeted in aceordanee with one or other
of the preceding examples.
Plate 114 as a whole is formed so that the axial
cavity 116 has a sufficient transverse dimension for a
cooling box 121 (preferably, but not exelusively, a
cooling box constructed in accordance with the arrangements
described in the parent patent).
33
` ` 116511~
It is thus possible to form cooling plate + box
assemblies which provide, in the same zone of the blast
furnace, cooling of the reEractory wall (deep cooling)
and cooling between the plating and the refractory wall
(surface cooling or thermal screen effect).
Fig. 17 shows the combination of such cooling assem-
blies (plate 114 + box 121) disposed in a sta~gered
arrangement with cooling boxes 122 alone (which may also
be preferably, but not exclusively, of the type described
in the parent patent) disposed in the sectors left free
(arrangement at the corners of a hexagon circumscribed on
plates 114).
It is thus possible to create veritable thermal
barriers, whose action extends not only in depth in the
refractory but on the surface and which, through the
arrangement oE the cooling boxes, provides good anchorage
for the refractory.
34
