Ring Seal With Overlapping Flanges for Contaminant Trapping

1. Field of Invention

This invention relates broadly to seals which prevent entrance of contaminants into various types of machinery, and more particularly, to seals between a rotatable shaft and a housing.

2. Prior Art

Many industries require the use of machines in which a rotatable shaft is contained by a housing. The housing usually contains lubricated bearings and sometimes additional attachments to the shaft such as turbine blades or gears. There are many types of seals provided between a shaft and a housing so as to prevent the leakage of lubricants from the housing and/or to prevent external contaminants from entering the housing along the shaft. In high speed operations of such rotating shaft mechanisms, contaminants to the internal lubricant result in increased wear, costly replacement of parts and, consequently, down time for the mechanism.

It is known to provide a sealing ring assembly comprising a first ring fixed to the housing and a second ring exterior to the housing and fixed to rotate with the shaft. Such an assembly is disclosed by U.S. Pat. No. 4,002,479, invented by David C. Orlowski and issued on May 10, 1977. In Orlowski, the first ring is held fixed to the housing by an o-ring and has an annular recess which matingly receives an annular flange of the rotating second member so as to allow free rotation without contact between the flange and the recess. The contaminants are theoretically discharged through an opening in the bottom of the recess in the first ring. The second ring is secured to the shaft by an o-ring. This arrangement has failed to prevent certain contaminants from entering the housing. An example of such a problem arises in the steam turbine industry, where such a seal is subject to an environment of steam, itself a contaminant, and also particles carried in the steam. In such an environment, steam easily penetrates the crevices between the first and second rings, condenses and is carried into the housing along the rotating shaft. An even greater contamination problem is created when the shaft is at rest and contaminants are allowed to build up and travel along the surfaces of the static rings to the static shaft which provides less frictional resistance to the contaminants than a moving shaft. A further problem arises when the o-rings or the sealing rings must be changed, which requires extensive down time while other components are removed in order to allow the sealing rings to be removed from the shaft.

Considering the above, it is an object of this invention to provide a ring seal between a housing and a rotatable shaft which prevents external contaminants such as steam from entering the housing, whether the shaft is rotating or static.

Still another object of this invention is to provide such a seal which requires relatively little time and effort to install and remove.

Still another object of this invention is to provide such a seal that will require relatively little service and infrequent replacement.

Still further objects and advantages of this invention shall become apparent from the ensuing descriptions of the invention.

Accordingly, a ring seal between a housing and a rotatable shaft is provided, comprising a plurality of ring members generally concentric with the shaft. A first ring member is fixedly and sealingly attachable within the housing and has an outer annular surface facing externally of the housing and an inner annular surface facing internally of the housing. A second ring member is positioned axially internal to the first member and is provided with an outer annular surface facing the inner surface of the first member and an inner annular surface facing internally of the housing. The second member is fixedly and sealingly attachable to the shaft so as to rotate relative to the fixed positon of the first ring member. The first ring member has an annular recess in its inner surface which receives an annular flange formed on the outer surface of the second member. A flange in the recess of the first member also forms a channel through which captured contaminants flow downward to an exit opening provided in the first member. The first and second ring members can be spilt so as to facilitate easy installation and removal. A third ring member is then provided which locks the second ring member into position and holds that position relative to the shaft and the first member.

FIG. 1 is a view of a typical arrangement in which the ring seals may be used.

FIG. 2 is a three-dimensional exploded view of a preferred embodiment of the invention.

FIG. 3 is a sectional view of a preferred embodiment of the invention in place between a housing and a shaft.

FIG. 4 is a sectional view of another preferred embodiment of the invention.

FIG. 5 is a sectional view of another preferred embodiment of the invention.

FIG. 6 is a sectional view of another embodiment of the invention.

FIG. 1 illustrates a typical setting in which the invention may be used, where a rotatable shaft 3 passes through machinery 1 and 2. In such an environment the interiors of the machinery 1 and 2 and possibly individual compartments within the machinery must be sealed in order to prevent entry of external contaminants which would enter along the shaft 3. The invention, generally denoted as 4, serves to provide such a seal.

As shown in FIG. 2, the three major components of the invention and preferred embodiments thereof are first ring member 5, second ring member 6 and third ring member 7. The three ring members 5, 6 and 7 are located between a housing 8 and the shaft 3 as shown in FIG. 3. The seal 4 prevents external contaminants from reaching an internal component such as a bearing 12. Of course, housing 8 may define a compartment within machinery 1, 2 as well as the exterior of shell machingery 1, 2. In such a case, the seal 4 could prevent migration of contaminants between compartments. The first member 5 is held fixedly 11 and sealingly in place within the housing 8. In the preferred embodiment shown in FIG. 3, this is accomplished by providing an outer annular fourth flange 9 which is held in place in a compatible groove 10 in the housing 8. In the embodiment shown in FIG. 4, the fourth flange 9 is located such that it it grips the inner surface of the housing 8. A similar flange 37 may be added to grip the outer surface of the housing 8. The center of the first ring member 5 is of large enough diameter to allow free rotation of the shaft 3 without contact with the first member 5. An annular space 11 is thus formed when the first member 5 is in place around the shaft 3. It is preferred that the perpendicular distance inside the annular space 11 from the shaft 3 to the first member 5 is 0.020 to 0.030 inches. The first member 5 is provided with a first flange 13 extending toward the interior of and axially adjacent to the housing 8. A second flange 14 also extends toward the interior of the housing 8, but is axially adjacent to the shaft 3. A third flange 15 extends radially inward from the first flange 13, thus forming an annular channel 16 in the first member 5. An opening 17 is provided at the lowest point in the channel 16, thus providing an exit point for contaminants to the atmosphere. At least one pressure relief hole 18 is provided in the second flange 14 in order to provide pressure equilibrium and prevent clogging in the channel 16.

The second member 6 is fixedly and sealingly attachable to the shaft 3 so as to rotate with the shaft. The second member 6 is located just to the interior of the housing 8 from the first member 5. In the preferred emodiment shown in FIG. 3, the second member 6 is provided with an annular recess 19 so as to compatibly receive the flange 13 of the first member 5, while allowing free rotation of the second member 6. In the preferred embodiment shown in FIG. 4, the first flange 13 of the first member 5 encases the second member 6. An annular flange 20 extends into the channel 16 axially adjacent to the second flange 14 of the first member 5. In a preferred embodiment, depressions 21 are provided in the surface of flange 20 adjacent to the third flange 14 of the first member 5. In another preferred embodiment, depressions 21 are also provided in the surface of flange 20 adjacent to the channel 16 of of the first member 5. It is preferred that the depressions 21 are arcuate in shape. The depressions 21 serve to promote the flow of contaminants to the exit point at opening 17. In a preferred embodiment, the exit opening 17 is at least as wide as the longest dimension of one of the depressions 21.

In another preferred embodiment, the inner surface 22 of the second member 6 is provided with threaded holes 23 and guide pin holes 24 running generally parallel to the shaft 3. The first member 5 is split into an upper half 25 and lower half 26. Correspondingly, the second member 6 is also split into an upper half 27 and a lower half 28. A third member 7 is provided in order to lock the upper and lower halves, 27 and 28, of the second member 6 together. The third member 7 is split into a left half 29 and a right half 30. For maximum strength, the plane between the left and right halves, 29 and 30, of the third member 7 should be generally perpendicular to the plane between the upper and lower halves, 27 and 28, of the second member 6. Locking screw holes 31 are provided through the third member 7, which are alignable with and of a diameter slightly larger than the threaded holes 23 in the second member 6. Locking screws 32 are provided which are insertable through locking screw holes 31 in the third member 7 and threadable into threaded holes 23 in the second member 6. Guide-pin holes 33 are also provided through the third member 7, which are alignable with guide-pin holes 24 of the second member 6. Guide pins 34 are provided which are insertable through guide pin holes 33 in the third member 7 and into guide pin holes 24 of the second member 6. Thus the upper half 27 and lower half 28 of the second member 6 may be aligned and locked together using the third member 7, guide pins 34 and locking screws 32. The upper half 25 and lower half 26 of the first member 5 are held in place by the housing 8. The ring members 5, 6 and 7 can then be easily removed without the necessity of removing other components which may be attached to the shaft.

In another preferred embodiment, threaded set screw holes 35 are provided through the third member 7 extending radially perpendicular to the shaft 3. Set screws 36 are threadable into the set screw holes 35 so as to bear against the shaft 3 and thus hold the axial positions of members 6 and 7 relative to the shaft 3. Set screws 36 may be provided for second member 6 as well.

Of course, other means, known in the art, of attaching members 5, 6 and/or 7 may be employed.

The second and third ring members, 6 and 7, recess 19 and flange 20 are of such a diameter so as to allow free rotation within, but with minimum outer clearance from, the housing 8 and the first member 5. Thus, as contaminants enter the annular space 11, they flow around the second flange 14 of the first member 5 and are trapped in channel 16 where they accumulate and flow back out to the atmosphere through exit opening 17. This flow of contaminants can occur whether the shaft 4 is rotating or static. If the shaft 3 is rotating, the indentations 21 serve to pick up the contaminants and pump them into the channel 16. The pressure relief hole 18 prevent excessive differential pressure from developing on either side of the second flange 14.

It is preferred that the first and second members, 5 and 6, be constructed of a material with anti-spark qualities, such as brass. In order to add strength to the assembly, the third member 7 should be constructed of a high strength material such as steel.

It is preferred that certain tolerances be maintained in order to assure the maximum sealing effect. The perpendicular distance between the outer surface 38 of flange 20 and the third flange 15 of first member 5 should be maintained at 0.032 to 0.062 inches. The axial perpendicular distance from the first flange 13 of first member 5 to second member 6 should also be maintained at 0.032 to 0.062 inches. The radial perpendicular distance from the first flange 13 of first member 5 to second member 6 should be maintained at 0.020 to 0.050 inches. The radial perpendicular distance from the third flange 15 of first member 5 to the flange 20 of second member 6 should be maintained at 0.010 to 0.015 inches. The depth of the channel 16 measured radially from the end of third flange 15 should be maintained at 0.040 to 0.060 inches. The internal diameter of the second and third members, 6 and 7, should be a maximum of 0.005 inches greater than the diameter of the shaft 3.

A preferred embodiment, useful in various pump designs, is shown in FIG. 5. In many pump configurations, bearings 12 are often located very near the exterior of the housing 8. The seal 4 must then be adapted such that it will fit in such a configuration. The position of the locking screws 32, threaded holes 23 and locking screws 31 may be reversed so that the locking screws 32 may be installed from the exterior of the housing 8. FIG. 5 is also illustrative of how the seal 4 may be installed without flanges such as those at 9 or 37 shown in FIG. 4. As can be seen in FIG. 5, the first flange of second member 6 is thickened and is sealingly engageable with shaft 3. Flange 20 has an exterior face 39 which faces the interior of first member 5. The second flange 14 of first member 5 is thereby eliminated. Contaminants or gases under pressure which flow along shaft 3 will be deflected and dissipated by exterior face 39.

To aid in contaminant removal an annular second flange 40 may be provided to aid in establishing contaminant flow, as shown in FIG. 6. Second member 6 and/or third member 7 may be provided with an annular groove 41 which may be filled with gasket material 42 to enhance the seal against shaft 3. The seal 4 may be utilized as a centrifugal throttling device, as shown in FIG. 6. The exterior of first member 5 is installed facing an existing mechanical seal assembly 43. Should the existing seal 43 fail, hot fluids under pressure would enter the seal 4 along shaft 3 and exit through opening 17 into exit port 44, safely venting the fluids away from shaft 3. The seal 4 replaces conventional packing as a blowout prevention device. Thus, explained earlier, the seal 4 may be installed facing either direction along shaft 3, depending upon the desired utility of the seal.

Thus, as can be seen, a ring seal is provided which allows for external contaminant removal whether the shaft is rotating or static. The seal is easily installable and removable without having to slide the seal off of the shaft. The seal is self-cleaning and self-locking, thus requiring little service and infrequent replacement. There are, of course, many alternate embodiments not specifically described but which are intended to be included within the scope of this invention as defined by the following claims.