Patent Grant
7673395
1. Field of the Invention
The present invention provides a method and apparatus for improving the drying uniformity of steam-heated cylinders. More particularly, the present invention provides a method and apparatus for improving the drying uniformity of steam-heated cylindrical dryers used in a papermaking machine.
2. Background Information
Paper is normally dried by passing it over a series of steam-heated, cast iron dryer cylinders. These cylinders are typically 4′, 5′, or 6′ in diameter, with some paper dryers being as large as 7′ in diameter. The steam inside the dryer cylinders transfers its heat to the paper through the dryer shell. As the heat is transferred from the hot steam to the wet paper, the steam inside the dryer condenses. The condensate thus formed is then removed from the dryer cylinder through a syphon pipe that is connected to an external pipe or tank through a rotating seal known as a “rotary joint”.
At low rotational speeds, the residual condensate inside the dryer will tend to accumulate in a puddle in the bottom of the dryer cylinder, in a “ponding” state. At higher dryer speeds, the condensate in this puddle will begin to rotate with the dryer shell, and then fall back into the puddle. This is normally referred to as the “cascading” state. At high dryer speeds, the condensate will follow the dryer cylinder around the entire periphery of the dryer shell, in a state that is called “rimming”. Most modern papermaking machines operate at speeds well above the speed at which the condensate goes through a transition from cascading into rimming. The subject invention is directed toward machines that operate above the “rimming speed”.
Syphon pipes are used to remove the condensate from the dryer cylinders during normal machine operation. The condensate must be removed at the same rate at which it is formed, to avoid filling up the dryer. There are two basic types of syphons as follows: 1/rotating syphons and 2/stationary syphons.
Rotating syphons are fixed to the inside surface of the dryer shell and rotate with the dryer. The outlet of the syphon pipe is maintained at a pressure that is lower than the steam pressure inside the dryer. This pressure differential helps to force the condensate into the syphon, up the radial syphon pipe, and out of the dryer. The differential pressure must be large enough to overcome the centrifugal force and lift the condensate from the rotating dryer shell and up to the dryer centerline. At high speeds, the centrifugal force can be quite large, requiring large differential pressures and large amounts of blow through steam. “Blow through” is that steam that enters the dryer cylinder and exits without condensing (that is, without contributing to drying the paper).
At high speed, even thin residual layers of condensate can form a significant resistance to the transfer of heat from the steam to the dryer shell. At high speed, the rimming layer of condensate is very stagnant and forms an insulating barrier between the steam inside the rimming condensate layer and the inside surface of the dryer shell. Variations in the thickness of the condensate layer can cause significant differences in heat transfer, resulting in non-uniform heating and drying of the paper. Rotating syphons are generally set with a small clearance between the syphon pick-up and the inside surface of the dryer cylinder. Small syphon clearances help to minimize the amount of residual condensate in the dryers and increase the heat transfer rate, but the resulting temperature profiles are still somewhat non-uniform.
Characteristics of the rotating syphons are as follows: 1/Close syphon clearances, 2/thin condensate layers, 3/high operating differential pressures, and 4/good heat transfer rates and temperature profiles (but not as high as a dryer with dryer bars).
Stationary syphons are the other type of dryer syphon. They are held in a fixed position (generally the 6 o'clock position) inside the dryer cylinder, just above the dryer shell. Such stationary syphons are held by a cantilever support tube that extends from an externally mounted rotary joint, through the hollow dryer journal, to the vertical syphon pipe. A stationary syphon pick-up is mounted at the end of the vertical syphon pipe. This pick-up is held above the rotating dryer shell surface with a small clearance in between the two. The stationary syphon can be equipped with a pick-up fitting that is shaped as a scoop. The scoop-shaped pick-up fitting uses the momentum of the rimming condensate to direct the condensate into the syphon pipe, up the vertical syphon pipe, and out of the dryer cylinder. The differential pressure required to remove condensate with a stationary syphon is much less than that required for a rotating syphon and the amount of blow through required for stable evacuation of the condensate is correspondingly reduced. The pick-up, however, tends to create turbulence in the rimming condensate. The turbulence in the vicinity of the syphon is greater than it is across the rest of the dryer shell. This increased turbulence produces a higher heat transfer rate through the condensate in the syphon area and a corresponding non-uniformity in the dryer surface temperature profile.
Characteristics of the stationary syphons are as follows: 1/Larger syphon clearances, 2/thicker condensate layers, 3/lower heat transfer rates, 4/poor temperature profiles, 5/low operating differential pressures, and 6/reduced blow through flow rates.
Dryer bars were developed to generate turbulence in the rimming layer, in order to increase the rate of convective heat transfer through the condensate layer. Dryer bars consist of a series of metal bars that are located inside the dryer cylinder. The bars are held by various means against the inside surface of the dryer cylinder. The bars tend to generate turbulence in the rimming layer of condensate that forms between the individual bars. This increase in condensate turbulence increases the rate of heat transfer and also tends to improve the uniformity of heat transfer from the dryer cylinder.
Barnscheidt and Staud first disclosed the concept of dryer bars in U.S. Pat. No. 3,217,426. Specific formulae for predicting the optimum spacing between bars was later added by Appel and Hong in U.S. Pat. No. 3,724,094. When the bars are positioned at or near the optimum spacing, the dryer bars will enhance the natural tendency for the condensate to slosh circumferentially. Near the optimum spacing, the condensate depth will be “in tune” with the bar spacing and a resonant sloshing motion will occur between the bars.
There are a number of prior art configurations of dryer bars. Most of the variations in these configurations are in the details of holding the bars to the inside surface of the dryer shell. One method, for example, uses a series of magnets to hold the bars to the dryer shell surface as taught by Mathews in U.S. Pat. No. 4,195,417. Another method uses a series of bars that are magnetic as disclosed by Wedel in U.S. Pat. No. 4,486,962. Other methods have been disclosed by Kraus in U.S. Pat. No. 3,808,700, by Schiel in U.S. Pat. No. 4,267,644, and by Schiel in U.S. Pat. No. 4,282,656, using various types of springs and pins.
In each of these prior art arrangements, the bars have consisted of solid metal bars. The number of rows of bars in each dryer cylinder is in the range of 18 to 36 for 5′ and 6′ diameter dryers. Bars used in commercial embodiments have square or rectangular cross-sections, ranging from 0.25″×0.25″ to as large as 0.5″×1″. The cross-section of the bars is selected based on such factors as the number of rows of bars in the dryer, the amount of condensate that is expected to be rimming inside the dryer, the cost of the bars, the rigidity of the bars, the specific system for holding the bars in place, and the ability to handle the bars during installation.
Most prior art bars are held against the dryer shell using a series of hoop segments. Various loading systems are installed between flanges at the end of the hoop segments, to force the segments apart and press the bars against the inside surface of the dryer shell. One of these systems is a simple threaded turnbuckle with locking nuts. Other, more sophisticated, designs use various coil, barrel, or Bellville washer springs between the hoop segments. A more recent development uses a unique compression bolt disclosed in co-pending application U.S. Ser. No. 10/151,407 filed May 17, 2002, now U.S. Pat. No. 7,028,756 issued on Apr. 18th 2006.
Dryer bars not only increase the rate of heat transfer through the condensate layer, but they also increase the uniformity of heat transfer. They can be used with either rotating or stationary syphons. The syphon clearance is selected to produce a residual condensate depth that will produce high heat transfer with the selected dryer bar configuration. By proper selection of the syphon clearance, the heat transfer rate under the stationary syphon pick-up can be matched to that of the dryer bars, producing a high dryer surface temperature and a uniform surface temperature profile.
More specifically, papermaking machines require a uniform dryer surface temperature profile in order to achieve a uniform cross-machine moisture profile in the paper that is produced. Dryer bars can be used to achieve this. Some papermaking machines, however, cannot operate with the correspondingly high dryer surface temperatures that are produced by the dryer bars.
The fibers in the wet paper of a fine paper machine, for example, will tend to stick to dryer surfaces that are too hot. This causes a “picking” phenomenon in which wet fibers are pulled off the sheet surface. This picking causes a loss in sheet quality, linting of the finished sheet, defects in the sheet surface, and poor machine runnability. The first few dryers following a size press or coater can have similar problems when the dryer surface temperatures are too high.
The conventional approach for these dryer cylinders is to reduce the steam pressure inside the dryers. This produces a corresponding reduction in steam temperature. The required steam pressures, however, may be lower than the dryer steam and condensate control system can achieve. Wet end dryers of newsprint and fine paper machines, for example, must often operate in a vacuum condition in order to achieve low enough steam temperatures. The vacuum condition is achieved using large heat exchangers that require large flow rates of cooling water to condense the blow through steam from the dryers and generate the vacuum inside the dryer.
At high dryer speeds, the vacuum condenser has to produce the required vacuum level in the dryers and also produce sufficient differential pressure to evacuate the condensate from the dryer.
This differential pressure required to evacuate the dryers and the resulting blow through flow rates can be quite large when using rotating syphons. The vacuum condenser often has inadequate capacity to generate the required differential pressure and handle the resulting blow through.
With stationary syphons, the differential pressure required to evacuate dryers and the resulting blow through is much less, so stationary syphons are often used in the wet end dryers of high-speed machines. However, with stationary syphons, the cross-machine dryer surface temperature profiles are quite non-uniform.
In order to achieve a uniform dryer surface temperature profile, dryer bars are generally used with stationary syphons. Conventional dryer bars, however, increase the rate of heat transfer and require a further reduction in operating steam pressure to achieve the same low dryer surface temperature.
What is required is a dryer bar configuration that can produce a uniform dryer surface temperature profile, but at the same time produce low dryer surface temperatures. This configuration is the subject of this invention. It can be used with rotating or with stationary syphons, but it has its best application to wet end dryers that have stationary syphons.
In order to achieve a uniform dryer surface temperature profile and a low heat transfer rate at the same time, in dryers with stationary syphons, the dryer bars of the subject invention are selected to operate at the quarter-resonance spacing.
The resonant spacing, as outlined in the prior art patent of Appel and Hong is given by the following equation:
S=π(Riδ)1/2
where:
S=Spacing between bars, inches
π=3.1415
Ri=Inside radius of the dryer shell, inches
δ=Average condensate depth in the dryer, inches
At the quarter-resonant condition, the spacing between bars would be four times larger than that given by the above equation. The corresponding condensate depth would be less than 10% of the value indicated by the above equation. The quarter-resonant spacing is given by:
S=4π(Riδ)1/2
The corresponding number of bars in the dryer cylinder according to this invention would be given by the following equation:
N=int{2πRi/(S+W)}
N=int{[2πRi/[4π(Riδ)1/2+W]}
Where:
int=Integer number of value in {brackets}
N=Number of bars in the dryer
W=Width of the dryer bars in inches.
The number of dryer bars must be an integer number. That is, the value in brackets in the above equations must be rounded either up or down to a whole number N. The number of bars that is used should be within 2 of the exact number calculated by the above equation.
The precise integer number can be selected based on practical considerations, as outlined later.
The rate of heat transfer will remain quite low if the number of bars in the dryer cylinder is significantly lower than that found in the prior art, and the condensate depth is not correspondingly increased. This is expected, based on prior art teaching. We have discovered, however, that the cross-machine heat transfer profile remains quite uniform when the dryer bars are operating at the quarter-resonant spacing, even though this is far from the spacing at which the dryer bars produce a resonant oscillation. This is a significant feature for those papermaking machines that require a low dryer surface temperature and the temperature uniformity of dryer bars.
The bars of the subject invention are held against the dryer shell using a series of hoop segments, as is done in most prior art configurations. In order to hold the bars tightly against the dryer shell, these hoop segments are pressed toward the shell surface using any one of a number of the prior art loading configurations.
The bars of the subject invention can alternately be solid bars or hollow tube bars. They may be mild steel or stainless steel. Stainless steel hollow tube bars are the preferred embodiment, as they are lighter in weight, they can be manufactured economically in stainless steel, and are stiffer than solid bars even when they are lighter in weight.
This invention was tested in a dryer cylinder that was 5′ in diameter and 246″ in width. As a benchmark, a commercial stationary syphon was installed in its normal location near the end of the dryer. The dryer was heated with steam and its surface subjected to a cooling load (simulating the drying of paper). The resulting dryer surface temperature profile was measured and recorded. The temperature profile is highly non-uniform in the cross-machine position, due to the high turbulence in the area of the stationary syphon and the thick condensate layer in the area away from the stationary syphon.
Commercial dryer bars were then installed in the same dryer, with the same stationary syphon, operating at the same dryer speed, steam condensing rate, and steam pressure. The resulting dryer surface temperature profile was measured and recorded. The dryer bars produced a significant improvement in the dryer surface temperature profile, as well as an increase in the temperature level. This demonstrates the effectiveness of dryer bars in correcting the non-uniformity in the dryer surface temperature profile, but also highlights the fact that the dryer surface temperatures increase significantly with dryer bars.
A second test was then conducted, again with a set of commercial dryer bars, again with a cantilever stationary syphon. The syphon clearance was set to achieve a condensate film thickness of approximately 0.25 inch, which was the optimum for the bar configuration, according to the prior art invention of Appel and Hong. The dryer steam pressure for these tests was set at 14.5 psig. The saturated steam temperature at this pressure is 248.8 degrees F.
The resulting temperature profile for this configuration indicated that the average dryer surface temperature profile was 225.4 degrees F. This value is quite high, as expected for a paper dryer with conventional dryer bars installed. The dryer surface temperature was only 23.4 degrees F below the steam temperature. The cross-machine heat transfer profile was again very uniform, as expected for a commercial dryer bar configuration.
Dryer bars with the configuration of the subject invention were then installed in the same dryer cylinder along with the same cantilever stationary syphon. The syphon clearance was set to achieve a condensate film thickness of approximately 0.25 inch. The optimum condensate depth, as prescribed by the prior art invention of Appel and Hong, would be approximately 3 inches.
The resulting temperature profile for this configuration indicated that the average dryer surface temperature profile was only 219 degrees F. This value is quite low, particularly considering that dryer bars were installed in the dryer. Specifically, the dryer surface temperature was 29.8 degrees F below the steam temperature. With conventional dryer bars, the average dryer surface temperature was 23.4 degrees F below the steam temperature. That is, the temperature drop for the dryer with dryer bars according to this invention was 26% higher than for the dryer with conventional dryer bars. This allows the dryer to operate with the same steam pressure, yet achieve a lower dryer surface temperature and fewer tendencies for picking, linting, and problems with runnability.
Not only was the dryer surface temperature lower than with conventional dryer bars, the cross-machine temperature profile remained flat. The standard deviation of the temperature profile was only 0.7 degrees F.
In the preferred embodiment of the subject invention, a 5′ diameter dryer is equipped with 6 hollow rectangular stainless steel bars, each disposed in an axial direction and each positioned and equally spaced adjacent to the inside surface of the paper drying cylinder.
The number of bars is significantly less than that taught by the prior art. Additionally, the condensate depth is significantly less than that taught by the prior art for this number of dryer bars. For example, in a 5′ diameter dryer cylinder, the typical prior art dryer bar configuration would have 18-32 rows of bars. The corresponding centerline spacing of the bars would range from 10″ down to 5.7″. The optimum condensate depths would range from 0.29″ to 0.08″.
In the preferred embodiment, the condensate depth would remain in the above range, but the bar spacing would be increased by a factor of 4. For example, a prior art dryer with a 57.75″ inside diameter and 18 rows of 1″ wide bars would have a spacing between bars of 9.08″. The optimum condensate depth according to the prior art would be 0.29″. In the preferred embodiment of this invention, the spacing between bars would be increased to 36.32″. This would require 4.9 bars in the dryer [3.1415×57.75″/(36.32+1)]. This value would be rounded to a close integer number (for example, to 3, 4, 5, 6, or 7).
In the preferred embodiment, each axial segment of bars is held against the dryer surface with hoop assemblies and each hoop assembly consists of 3 segments. In the preferred embodiment, there is one threaded fastener between each of the hoop segments. Each fastener has one threaded nut, for tightening the hoops, and one back-up jam nut. The hoop segments are attached to the rectangular dryer bars with pins. This configuration is disclosed in the aforementioned co-pending application.
With the preferred embodiment, each of the hoop segments would be identical if the number of bars selected according to the present invention is 6. This is the closest integer number of bars that is directly divisible by the number of hoop segments (6/3=2 bars per hoop segment).
Because of the number of bars in the present invention is significantly less than those used in the prior art, the span between bars is correspondingly much longer. In order to prevent the hoop segments from bowing between the bars, short spacers are placed under the hoops between bars. These spacers support the hoop segments between the bars and prevent the hoops from bowing.
In the method according to this invention, the dryer surface temperature profile is improved while the dryer surface temperature level is kept low, by installing a small number of bars in the dryer cylinder and maintaining a low level of condensate in the dryer.
Therefore, it is a primary feature of the present invention to provide a dryer bar apparatus for a dryer that overcomes the problems associated with the prior art arrangements.
Another feature of the present invention is the provision of a dryer bar apparatus that reduces the number of dryer bars.
A further feature of the present invention is the provision of a dryer bar apparatus that maintains cross-machine direction temperature uniformity while decreasing the transfer of thermal energy.
Other features and advantages of the present invention will be readily apparent to those skilled in the art by a consideration of the detailed description of a preferred embodiment of the present invention contained herein.
The present invention relates to a dryer bar apparatus of a dryer for drying a web in a papermaking machine. The apparatus includes a rotatable dryer shell of cylindrical configuration, the dryer shell having an outer surface for drying the web. The dryer shell has an inner surface which defines an enclosure, the inner surface having a radius Ri. The enclosure is connected to a source of pressurized steam such that in operation of the dryer, a transfer of thermal energy from the steam within the enclosure through the inner surface of the dryer shell to the outer surface of the dryer shell is achieved so that the web is dried. A syphon is disposed within the enclosure for controlling a layer of condensed steam accumulating adjacent to the inner surface of the dryer shell during operation of the apparatus. A number of turbulance bars are disposed within the enclosure, each of the turbulance bars extending in a cross machine direction in contact with the inner surface. The bars are circumferentially spaced equidistantly around the inner surface of the dryer shell for generating turbulance within the layer. The arrangement is such that uniformity of the transfer of thermal energy in the cross machine direction is maximized while the transfer of thermal energy through the dryer shell from the inner to the outer surface is minimized. Also, the number of turbulance bars is determined by the equation:
N=int{2πRi/[4π(Ri/δ)1/2+W]}
in which:
N=the number of turbulance bars in the dryer shell;
int=an integer number of a value in { } brackets;
π=3.1415;
Ri=the inside radius of the inner surface of the dryer shell in inches;
δ=an average depth of the layer in inches;
W=a width of each of the turbulance bars in inches.
In another aspect of the present invention a dryer bar apparatus of a dryer for drying a web in a papermaking machine, includes a rotatable dryer shell of cylindrical configuration, the shell defining an outer and an inner surface. A number of dryer bars are pressed outwardly against the inner surface, each of the bars extending in a cross-machine direction along the inner surface. Each bar is spaced from an adjacent bar by a quarter-resonant spacing such that a rate of heat transfer through the dryer shell from the inner to the outer surface is minimized while optimizing a temperature uniformity in the cross machine direction. The quarter-resonant spacing is determined by an equation:
S=4π(Riδ)1/2 in which;
S=the quarter-resonant spacing;
π=3.1415;
Ri=the inside radius of the inner surface of the dryer shell in inches;
δ=an average depth of a layer of condensed steam disposed adjacent to the inner surface in inches.
In a more specific embodiment of the present invention, the apparatus includes dryer bars. A cross-section of each of the bars is within a range from 0.25 inches×0.25 inches to 1.0 inches×1.50 inches. Each of the bars is metallic and of hollow tubular configuration. The apparatus includes at least one hoop for pressing each of the bars against the inner surface of the dryer shell. The at least one hoop includes at least one segment.
Also, the at least one hoop includes a number of segments within a range 2 to 4, each segment having a first and a second end. A segment fastener is disposed between the first and second end of the segment for forcing adjacent segments apart. Each fastener is threaded on one of the ends thereof. Each of the hoop segments defines a hole in each end thereof, for engagement with a segment fasteners. Each of the segment fasteners has a head that passes through the hole in the end of the segment. A hexagonal socket head is defined by the fastener for permitting tightening of the fastener by a power tool. A cylindrical pin is provided for connecting each of the bars to an adjacent segment.
More specifically, the pin has an interference boss to hold the pin in the segment. The pin extends far enough out of the segment and into the bar so that disengagement of the pin from the segment is prevented.
The present invention also provides a method of improving a cross-machine directional heat transfer profile of a papermaking dryer cylinder. The method includes the steps of holding a number of bars axially against an inside surface of the dryer cylinder, the number being within a range 3 to 9. Hoop segments are then located within the dryer cylinder such that each segment is disposed in a generally circumferential position.
The dryer bars according to the present invention are also applicable to other dryer diameters, including small paper dryers and large (Yankee) tissue dryers.
Many modifications and variations of the present invention will be readily apparent to those skilled in the art by a consideration of the detailed description contained hereinafter taken in conjunction with the annexed drawings which show a preferred embodiment of the present invention. However, such modifications and variations fall within the spirit and scope of the present invention as defined by the appended claims.
a is an enlarged view of the fastener shown in
b is a view taken on the line 9b-9b of
c is an enlarged view of a cylindrical pin for connecting each bar to an adjacent segment;
Similar reference characters refer to similar parts throughout the various views of the drawings.
N=int{2πRi/[4π(Riδ)1/2+W]}
in which:
N=the number of turbulance bars 18 to 23 in the dryer shell 12;
int=an integer number of a value in { } brackets;
π=3.1415;
Ri=the inside radius of the inner surface 16 of the dryer shell 12 in inches;
δ=an average depth of the layer 32 in inches;
W=a width of each of the turbulance bars 18-21 in inches.
In a more specific embodiment of the present invention, the number N of turbulance bars is equal to N±1. However, in another embodiment, the number N of turbulance bars is equal to N±2.
As shown in
In another aspect of the present invention as shown in
S=4π(Riδ)1/2 in which;
S=the quarter-resonant spacing;
π=3.1415;
Ri=the inside radius of the inner surface 16 of the dryer shell 12 in inches;
δ=an average depth of a layer 32 of condensed steam disposed adjacent to the inner surface 16 in inches.
In a more specific embodiment of the present invention as shown in
Also, the at least one hoop includes a number of segments 24-26 within a range 2 to 4, each segment such as segment 24 having a first and a second end 48 and 50 respectively.
a is an enlarged view of the fastener 52 shown in
b is a view taken on the line 9b-9b of
c is an enlarged view of a cylindrical pin for connecting each bar to an adjacent segment. As shown in
More specifically, the pin 65 has an interference boss 67 to hold the pin 65 in the segment 24. The pin 65 extends far enough out of the segment 24 and into the bar 18 so that disengagement of the pin 65 from the segment 24 is prevented.
The specific configuration of the segment fasteners is disclosed in the aforementioned co-pending application, now U.S. Pat. No. 7,028,756 issued on Apr. 18th 2006. All of the disclosure of the aforementioned application now U.S. Pat. No. 7,028,756 issued on April 18th 2006, is incorporated herein by reference.
The present invention also provides a method of improving a cross-directional heat transfer profile of a papermaking dryer cylinder. The method includes the steps of holding a number N of bars 18 to 23 axially against an inside surface 16 of the dryer cylinder 12. The number N is within a range 3 to 9. Hoop segments 24-26 are then located within the dryer cylinder 12 such that each segment 24 to 26 is disposed in a generally circumferential position.
The dryer bars of the subject invention provide improvements in the dryer surface temperature profiles in the cross-machine direction while simultaneously maintaining low dryer surface temperatures. The invention can be used in those paper dryers that require improved dryer surface temperature profile uniformity, but also require low surface temperatures. The low dryer surface temperatures help to reduce the tendency for the wet sheet to pick, cause Tinting and dusting, and cause problems with sheet runnability. The invention is particularly useful for improving the profile uniformity in those dryer cylinders that are operating above the condensate rimming speed, with stationary syphons.
| Number | Name | Date | Kind |
|---|---|---|---|
| 3217426 | Barnscheidt et al. | Nov 1965 | A |
| 3724094 | Appel et al. | Apr 1973 | A |
| 3808700 | Kraus | May 1974 | A |
| 4195417 | Mathews | Apr 1980 | A |
| 4267644 | Schiel | May 1981 | A |
| 4282656 | Schiel | Aug 1981 | A |
| 4478168 | Wimmer | Oct 1984 | A |
| 4486962 | Wedel | Dec 1984 | A |
| 5564494 | Salminen | Oct 1996 | A |
| 7028756 | Ives et al. | Apr 2006 | B2 |
| Number | Date | Country | |
|---|---|---|---|
| 20060179677 A1 | Aug 2006 | US |
