YANKEE DRYER WITH HOOD APERTURE RATIO

SECHOIR DE MACHINE A PAPIER A OUVERTURE DE CAPOT REGLABLE

English Abstract

ABSTRACT OF THE DISCLOSURE
Method and apparatus for drying a moving web
utilizing one or more air caps each including an apertured
plate together with a high pressure plenum which is arranged
to deliver high pressure air through the apertures in the
plate to impinge against the web. The geometry of the plates,
their spacing from the web and the positioning of exhaust
means are correlated to provide a minimum amount of cross
flow interference thereby improving the heat transfer and
ultimately the efficiency of the drying operation.

Claims

THE EMBODIMENTS OF THE INVENTION IN WHICH AN EXCLUSIVE
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. An apparatus for drying a moving web comprising a high
pressure plenum, a plurality of apertured plates extending
across the width of the web to be dried, conduit means enclosing
each of said plates and connecting the same to said plenum, each
of said plates being spaced from adjoining plates along its
entire periphery thereby providing exhaust channels for air
streams impinging against said web so that air exhausting between
the plates prevents cross flow interference of spent air with air
streams, said conduit means having a cross-sectional area of
lesser extent than the cross-sectional area of its associated
plate inwardly of said plate in the direction of said plenum
thereby providing an extended exhaust space between said plates
and said plenum, and a common exhaust conduit communicating with
said exhaust space, said conduit extending through and beyond
said plenum.
2. An apparatus for drying a moving web constructed in
accordance with claim 1, wherein said openings have a diameter
in the range of 1/16 inch to 3/4 inch and have an area of no greater than
3% of the area of the plate.
3. An apparatus for drying a moving web constructed in
accordance with claim 1, wherein said plate apertures comprise
openings having a diameter D and having a distance Z from the
web, the ratio Z:D being no greater than 6.
4. An apparatus for drying a moving web constructed in
accordance with claim 1, wherein the ratio of the distance of
14

the apertures from the surface of the web to the diameter of
the apertures is in accordance with the following table:
<IMG>
5. An apparatus for drying a moving web comprising a high
pressure plenum, a plurality of apertured plates extending across
the width of the web to be dried, conduit means enclosing each
of said plates and connecting the same to said plenum, each of
said plates being spaced from adjoining plates along its entire
periphery thereby providing exhaust channels for air streams
impinging against said web, said conduit means having a cross-
sectional area of lesser extent than the cross-sectional area of
its associated plate inwardly of said plate in the direction of
said plenum thereby providing an extended exhaust space between
plates and said plenum, and a common exhaust conduit communi-
cating with said exhaust space, said conduit extending through
and beyond said plenum, the open area of the apertures in said
plate constituting no more than about 3% of the area of said
plate, the ratio of the distance of the apertures from the surface
of the web to the diameter of the apertures being in accordance
with the following table:
<IMG>

6. The apparatus of claim 5 in which the apertures in said
plates are smoothly contoured to reduce flow disturbances.
7. The apparatus of claim 5 in which said plates are
substantially square and the length of one side of the square
is no more than about 1.8 times the diameter of an aperture
divided by the open area.
16

Description

~- 103~ 4~
BACKGROUND OF THE I~IVENTION
-
Field of the Invention
This invention i9 in the field of drying by means
of impingement flow of high pressure heated air, with provisions
i being made for exhausting the impinging air streams behind the
impingement jets so that the impinging air streams are directed
to an exhaust chamber at a relatively low velocity and without
excessive pressure drop.
DESCRIPTION OF THE PRIOR ART
.~ .
Impingement flow, that is, flow directed normal to
the surface has been recognized as an efficient means for heating
or cooling. In recent years, this method of heat transfer has
been used in the paper industry for drying of paper. Representa-
:., -
tive patents in this field are U.S. Patents Nos. 3,163,502,
issued December 29, 1964 to Justus et al, 3,167,408, issued
January 26, 1965 to Justus et al, and 3,447,247, issued ~une 3,
1969 to Deane, all owned by the assignee of the present invention.
Air impingement drying is particularly suited for
drying of lightweight grades of paper such as tissue paper and
:~:
e~ 20 for drying coated paper. These applications require higher rates
,~ of heat transfer because of the limited drying length and the
requirements of high speed operation.
There are various types of air impingement devices
in use on paper drying apparatus. One of these types uses slotted
,, .
nozzles and another incorporates round holes to provide jet
orifices for impingement purposes. The slot nozzle arrangements
have the disadvantage of requiring a relatively complex system
i~, .
of air removal ducts be~ween the slots. Slot arrangements are
also characterized by inefficient performance as measured by
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1036348
the heat transfer coeficient obtainable for a given expenditure
of air blower horsepower. In addition, relatively small spacings
between the impingement surface and the ~lot nozzles are required
in order to obtain good heat transfer results.
Some o~ the disadvantages inherent in the slot nozzle
arrangement are eliminated in the round hole impingement systems.
For example, the heat transfer coefficient is relatively unaffec-
ted by the distance from the nozzle to the impingement surface as
long as there is a proper ratio of the impingement distance to
the hole diameter. Also when using round impingement holes, it
becomes easier to incorporate air exhaust systems between sets
of the round holes.
With the demand for increased machine speeds, adequate
drying must either be accomplished by raising the drying rate or
the heat transfer length. Increased drying lengths require
additional capital expenditure for already expensive dxying
equipment. In tissue drying applications, where the wet web i8
pressed on the surface of a large diameter rotating drum, the
web must be dried in less than one revolution. Typically, such
a drying system employs a large diameter steam filled cylinder
surrounded by a high temperature, high velocity air impingement
cap. However, these steam filled cylinders are already opera-
ting at about the highest practical diameter possible. There-
fore, any further increases in speed must come from increased
heat transfer rates from air impingement. At the present time,
- air caps are being operated at temperatures of about 800F.
In order to achieve higher temperatures, expensive hi~h tempera-
ture alloys must be employed. In addition, at these higher
temperatures problems are encountered in maintaining the

-- ~V3~;34~
dimensional stability of the equipment and as impingement
temperatures get higher, more problems will ~e encountered with
drying uniformity.
Inasmuch as air caps in u~e today in the paper industry
are already operating at about the limit of temperature, it
becomes necessary to increase the convective heat transfer
coefficient in order to increase the heat transfer rate and
consequently the evaporation rate. In paper drying applications,
a large convective heat transfer coefficient helps to alleviate
any nonuniorm drying problems. One method of increasing the
convective heat transfer coefficient i~ sLmply by increasing
the impingement velocity. However, for a given system configura-
tion an increase in ~mpingement velocity can only be obtained
at the expense of increased fan horsepower. Increases in fan
horsepower represent both increased capital cost for equipment
and also increased operating expense. Therefore, an upper limit
exists whereby increases in heat transfer rate by adding
additional fan horsepower are no longer considered fea~ible.
- Another means of increasing the heat transfer coef-
~0 ficient is to increase the number of impinging jetsO that is,
by increasing the open area of the impingement plate. Published
literature indicates that after the open area is increased
beyond approximately 2%~ no further gains in the heat transfer
rate are obtainable. It was thought that the inability to
; improve the heat txansfer rate was caused b~ interference
~,...
between adjacent impinging jetsr that is, as the open area was
increased and the impingement jets became closer and closer
together, it was thought that the adjacent jets interfered
with each other thereby reducing the heat transfer coefficient.

103639~8
More recently published experimental data indicates
that this reduction in heat transfer coefficient is not caused
by interference between adjacent jets but rather by cross flow
interference from the spent air. The jets after impingement
must travel to an opening to be exhausted and this means that
the spent air must travel across adjacent jets before reaching
an exhaust outlet. This exhaust cross flow interference can
actually cause the impinging jet to be bent at an angle which
i9 not perpendicular to the surface of impingement. Any devia-
tion of the impingement jet from a line normal to the heated orcooled surface results in a degradation o~ the heat transfer
rate. consequently, it becomes important to eliminate or
, reduce cross flow interference if the average heat transfer
coefficient is to be increased.
SUMM~RY OF THE INVENTION
The present invention is directed to ~ mothod lnd
E,DD
apparatus for impingement drying involving a correlation between
the variables involved in such drying as well as structural
; features which minimize cross flow interference between adjoin-
ing jet orifices. One of the features of stxucture involved is
the provision of a support housing for the apertured plate which
is of lesser cross-sectional area than the plate so that the
area behind the individual plates serves as an extended area
exhaust region in which the impinging air streams are directed
: '
at a relatively low velocity and without an excessive pxessure
drop. ~nother structural feature involve~ the use of an array
, . .
consisting of a plurality of apertured plates with exhaust
regions located about the entire periphery of each plate so
that any given apert~re in the plate is not spaced an excessive
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~03~;34~
distance from an exhaust region. Also contributing to the
improved efficiencies of the present invention are an improved
aperture configuration. For best results, we have found it
desirable to space each jet aperture an equidi6tant amount from
the next adjacent jet aperture as by providing a pattern of
apertures which is a series of squares or a series of equi-
lateral triangles.
As far as operating parameters are concerned, we have
found that the open area of the apertures in the plate should
preferably constitute no more than about 3~ of the area of the
plate and that the diameter of the apertures should preferably
be within the range from about 1/16 inch to about 3/4 inch. It
is also desirable to correlate the ratio of the distance of the
aperture from the surface of the web to the diameter of the
aperture such that with greater open areas, the ratio of
f distance to diameter is lower.
Basically, the preferred embodiments of the present
invention provide small diameter impingement holes over the
~ntire impingement plate to achieve large heat transfer rates
per unit area. The arrangement is such that there is a relat-
ively large open area to obtain a large number of heat transfer
spots. Exhaust openings are provided on all sides of the
impingement plate to minimize any cross flow interference.
Another feature involves the use of a central high pressure
plenum to feed each of the impingement boxes uniformly. Other
` improvements are achieved by utilizing tapered impingement
boxes and smoothly contoured inlets for feeding the high pressure
air through the apertured plates.
BRIEF DESCRIPTION OF THE DRAWINGS
~ 30 Other objects features and advantages of the invention
,',-:~
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103~;3~
will be readily apparent from the following description of
cert~in preferred embodiments thereof, taken in conjunction
with the accompanying drawings, although variations and
modifications may be effected without departing from the spirit
and scope of the novel concepts of the di6closure, and in which:
Figure 1 is a somewhat schematic view illustrating an air
cap system of the present invention associated with a large
diameter Yankee drier drum;
Figure 2 is a fragmentary vertical cross-sectional view of
the bell-shaped support means for the perforated plate;
Figure 3 is a fragmentary view partly in elevation and
partly in cross-section of one of the bell structures as shown
in Figure 2;
Figure 4 is a fragmentary cross-sectional view of the type
of apertured plate used in the structure of Figures 2 and 3;
Figure 5 is a fragmentary cross-sectional view on an
enlarged scale taken substantially along the line V-V of Figure
4.
Figure 6 is a cross-sectional view taken along the line
VI-VI of Figure 2; and'
Figure 7 (same sheet as Figure 1) is a schematic view,
partly broken away illustrating another air cap structure
produced according to the present invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Before proceeding with a detailed description of the
drawings, it would be well to review the inter-relationæhip
between the variables involved in an impingement drying process.
As mentioned previously, cross flow interference from the spent
-~ air provides a significant reduction in the average heat transfer
coefficient of the system. One means of alleviating the cross
'
- 6 -

1()3~3~
flow interference wo~ld be to pro~ide exhau~t openings at or
near impinging jets, but this results in a very complex and
expensive system. It is also desirable to provide as many heat
transfer spots as possible. For a given open area this can be
accomplished by incorporating small diameter impingement holes.
It has been found that small diameter holes are more susceptible
to cross flow interference. As the cross flow velocities are
increased, the small diameter jet can easily be bent or even
destroyed by the cross flow. Larger diameter jets are less
susceptible to this interference because of the larger momentum
associated with the jet.
- Another problem associated with utilizing small diameter jets
is that the distance from the impingement plate to the surface
to be heated or cooled must be kept at a relatively small value
in order to avoid a reduction in heat transfer. At very small
spacings, a pressure buildup can occur at locations away from
the exhaust openings. This results in the establishment of a
large pressure drop between the area at which the jet impinges
' and the point at which the spent air is exhausted. At points
where the pressure is high impingem0nt velocities are low, and
at points where the pressure is low, higher impingement velocities
occur. The reason for this is that the plenum pressure is
constant and the impingement velocity is controlled by the
pressure differential acros~ the impingement plate. This results
:
in nonuniform heat transfer and ultimately nonuniform drying.
We have now managed to correlate these inter-acting variables
and provide an integrated system in which high heat transfer
- rates are obtained with a minimum of cross flow interference
into the exhaust openings. Through the particular arrangement
-- 7 --
;~ .
,.

-`: 1()3~ 48
to be discussed, we have managed to minimize the pres6ure
gradient between jets located at varying distances from the
exhaust openings.
Turning to specifics, we have found that the open area of
the apertures in the impingement plate should constitute no more
than about 3% of the area of the plate. We have also ound that
the diameter of the apertures should be in the range from about
1/16 inch to about 3/4 of an inch. Furthermore, our work has
; determined that the ratio of the distance of an aperture from
; 10 the surface of the web to the diameter of the aperture for best
results, should be in accordance with the following table:
TABLE 1
OPen Area Ratio of Distance/Diameter
up to 1% 3 - 6
greater than 1%
up to 2% 2 - 5
greater than 2%
up to 3% 2 - 4
In order to secure uniform heat transfer across the web,
it is desirable that the apertures be symmetrically disposed
within ~he plate, with each aperture being equidistant from
the adjacent apertures. We accordingly prefer to provide a
pattern of apertures which constitutes a series of squares
or a series of e~uilateral triangles.
The plates in which the apertures are located are prefer-
ably substantially square. In order to provide access of the
centrally disposed apertures in the plate to the peripheral
exhaust area surrounding the plate, it is advisable to make the
- length of one side of the square plate no more than about 1.8
times the diameter of an aperture divided by the open area.

`` 103~;;~48
A-~ a specific example, for a plate having aperture~ of 1/~
inch in diameter and an open area of 0.0276 (2.76O the maxi-
mum length of a side of the s~uare plate would be about 8.15
inche~.
!`~ Turning now to a specific description of the drawings, in
Figure 1 there is illustrated a drying assembly of the type
which is used for drying lightweight webs such a~ tis~ue paper
and the like. The drying assembly includes a large diameter~:,
steam heated Yankee-type drier roll 10 to which a web of tissue
or the like i~ applied by means of a conveyor belt 11 trained
around a roller 12. As illustrated in Figure 1, the web of
tissue travels around a major portion of the periphery of the
drum 10 and is removed therefrom by means of a doctor blade
'. 13 and wound up on a takeup roll 14.
The drying assembly of Figure 1 includes a pair of air cap
assemblies which are positioned in clo~e proximity to the sur-
face of the traveling web and extend the full width of the web.
O. High pressure heated air is ~pplied from a so~rce (not shown)
to an inlet manifold 15 which delivers the air to conduits 16
$. 20 and 17 located in spaced relation along the arcuate periphery
of the air cap assembly, thereby providing a high pressure
~ plenum 18 from which a plurality of bell-shaped plate supports
.. 19 are fed. The configuration of these supports 19 is best:'
~: illustrated in Figures 2 to 6 of the drawings from which it
will be seen that the supports 19 are formed with a rounded
::
':.; entrance portion 20, a relatively small diameter throat portion
21 and a flared bell-shaped bottom portion 22 in which there i~
'
located an apertured plate 23. A series of dimples 24 and
~, .
~; tabs 25 are provided at the periphery to confine the plate
,
_ g _
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103~;348
23 tightly within the base of the bell-shaped portion.
The plate 23 contains apertures 26 in symmetrically dis-
posed array which constitutes a square pattern as illustrated
in Figure 4. The inlet end of each of the apertures 26, as
illustrated in Figure S has a contoured entrance 27 to minimize
flow irregularities and turbulence.
The high temperature high pressure air passing through the
apertures 26 in the plate 23 impinges against the web on the
surface of the drum 10 with very substantial velocities on the
order of 20,000 to 30,000 feet per minute. A typical web ~peed
of lightweight paper would be about 4,000 to 6,500 feet per
minute. The impinging air after striking the surface of the
web is deflected around the periphery of each of the bell-shaped
supports 19 into the region between the relatively narrow throat~
21 which region is an exhaust region identified at reference
numeral 28 in the drawings. The exhaust region 28 is in fluid
communication with an exhaust conduit 29 as illustrated in
both Figures 1 and 2. Each of the exhaust conduits 29 has a
rounded inlet portion 30 and an outwardly tapered body portion
31, the function of which is to provide as low a pressure drop
as pos~ible and as little turbulence as possible in the flow
of the exhausted air. The exhausted air is directed into a
plenum chamber 32 from where it is removed by means of an
exhaust conduit 33.
- ~he other air cap structure illustrated in Figure 1 is
substantially identical to that described and the corresponding
elements of this structure are identified with the same refer-
; ence numerals as used previouæly, followed by the subscript "a".
',:
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103~348
Another arrangement of apertured plates for high velocity
impingement drying is illustrated in Figure 7 of the drawings.
In the form of the invention there illustrated, a plurality
of generally square plates 34 each having an array of apertures
arran~ed in a square pattern are received in support mean-
~including inwardly curved side walls 35 which fasten to rela-
tively small diameter pipe~ 36. The ends of the pipes 36 are
fastened to a wall 37, the ends having a smoothly rounded lip
38. A wall 39 is spaced from the wall 37 to provide a high
pressure plenum chamber 40 therebetween for introducing high
pressure heated air through the pipes 36 and thence through
the perforated plates 34. The complete array may include
twenty-four to thirty-six plates or so and centrally of the
array of plates there is left a blank exhaust area 41. An
exhaust conduit 42 having a tapered end portion 43 communicates
with the exhaust area 41 to vent the exhaust air therefrom.
With both of the forms of the invention shown, it will be
apparent that the impingement air is directed rearwardly about
the entire peripheries of the plates to a single exhaust means
thereby providing a relatively large area for exhaust flow
resulting in a relatively low exhaust velocity and the absence
of an excessive pressure drop.
Various types of plenum arrangements may be made to take
advantage of the improvements of the present invention. For
example, the air exhausted into the exhaust area behind each
plate can be directed to a large exhaust area located between
adjoining plenums where the combined exhausts from the adjoining
plenums are combined and vented.
Calculations have determined that air cap structures

1036348
including the improvements of the present invention are con-
~iderably more efficient for drying purposes than other air
caps presently available. These calculation~ were based on
drying a tissue paper having a weight of 12 pounds for 3,000
square feet and an initial moisture content of 1.5 pounds of
water for every pound of fibers. The air caps would be
located about a Ya}~cee drier of 16 feet in diameter and occupy
270 degrees of the circumference of the drier drum. In both
cases, the steam temperature within the drier drum was taken
as 345 F, and the impinging air was to be at a temperature of
800F. In both cases, the impingement velocity was assumed to
to be 25,000 feet per minute.
With a commercially available air cap device, the jets
have an open area of 0.0147 ~1.47%) and a jet diameter of
0.375 inch. The vertical spacing of the jets is 1 inch from
the surface of the web. The i~pingement heat transfer coefficient
was calculated to be 56.1 BTU per hour, per square foot, per
degree F. Under these conditions, the web could be dried
at a machine speed of 5,154 feet per minute.
With the new design of air cap, the open area is taken as
0.0276 (2.76%) and the jet diameters at 0.125 inches. The
vertical spacing from the jet to the web was to be 1/2 inch.
It was calculated that under these conditions, the impingement
heat transfer coefficient would be 83.7 13TU per hour, per
,.
square foot, per degree F. Under these circumstances, the
' paper could be dried to the same degree of moisture content
at a machine speed of 6,873 feet per minute, thereby increasing
the deying speed by a factor of more than 30%.
At the same open area and impingement velocity, the heat
12
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;348
transfer coefficient for the 1/8 inch jet array i8 approxl-
mately 30~ higher than ~he 3/8 inch jet array at the same
power consumption.
Thus, with the arrangement above described, increased
heat transfer from the drying air to the moist web, and hence
increased evaporation is achieved. A reduction of the
deleterious effects of cross flow upon the heat transfer
coefficient is achieved. In partial summary of the above,
the openings have a diameter D in the range of 1/16" to 3/4".
The distance z of the openings to the supporting surface is
related to the size of orifice openings so that the ratio
of Z:D is no greater than 6. By increasing the spacing
between the orifices and the support, the cross flow velocities
of the escaping air are decreased. It has been found that
heat transfer is relatively unaffected by vertical distance
as long as the ratio of Z:D is equal to or less than 6.
~ 13 ~
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