Patent Abstract:
A viscous seal for fluid transfer devices that deviates from the conventional wisdom of avoiding contact between the seal and a rotating drive shaft of the fluid transfer device. Instead of avoiding contact, contact between the seal and drive shaft is used to effect axial alignment of a sealing sleeve with the shaft. As a result, the viscous seal is compliant in that the sealing sleeve can follow the axis of the drive shaft. Accordingly, the sealing sleeve can fit snugly around the drive shaft for more effective prevention of leakage of low or any viscosity fluid along the drive shaft, but without any significant radial load being applied to the sealing sleeve that might cause undue wear or damage due to galling.

Full Description:
This application claims the benefit of U.S. Provisional Application No. 60/483,570 filed on Jun. 27, 2003, which is hereby incorporated herein by reference in its entirety. 

   The present invention relates generally to fluid transfer devices and more particularly to a seal for preventing fluid leakage along a drive shaft of the device. 
   BACKGROUND OF THE INVENTION 
   Shaft seals are known devices to prevent fluid leakage along a drive shaft of a pump, motor or other fluid transfer device. One known type of shaft seal is a viscous seal. The viscous seal acts like a screw pump, forcing any leaking fluid back into the housing of the fluid transfer device. In a conventional design, the viscous seal is attached to the housing and the drive shaft rotates within a bore in the housing that is sealed by the viscous seal. The viscous seal, if working properly, will not be lubricated by the leaking fluid over its entire length since the leakage will be stopped before reaching the outboard end of the seal. Thus, the drive shaft and the viscous seal will be dry and free from lubrication over a portion thereof. For this reason, prior art viscous seals are designed not to contact the drive shaft to prevent damage to the seal or galling of the drive shaft. The effectiveness of the seal is directly proportional to the radial gap between the seal and the drive shaft. The seal can be made more effective by reducing the gap. 
   Prior art viscous seals have been effective for preventing leakage of relatively viscous fluids having a viscosity of about 10,000 centipoise or higher. The effectiveness of viscous seals, however, decreases as the viscosity of the leakage fluid decreases. At relatively low viscosities on the order of about 100 centipoise, other means are needed to increase the effectiveness of the viscous seal. As above noted, viscous seal performance can be improved by decreasing the clearance between the drive shaft and the seal, but there are practical limits to maintaining the alignment between the drive shaft and seal in order to prevent contact between the drive shaft and seal. Another technique is to increase the viscosity of the leakage fluid at the seal by cooling the fluid, either actively or passively. The known cooling techniques, however, may not always be suitable for a given application or can introduce undesired additional cost and/or maintenance. 
   SUMMARY OF THE PRESENT INVENTION 
   The present invention provides a viscous seal for fluid transfer devices that deviates from the conventional wisdom of avoiding contact between the seal and a rotating drive shaft of the fluid transfer device. Instead of avoiding contact, contact between the seal and drive shaft is used to effect axial alignment of a sealing sleeve with the shaft. As a result, the viscous seal is compliant in that the sealing sleeve can follow the axis of the drive shaft. Accordingly, the sealing sleeve can fit snugly around the drive shaft for more effective prevention of leakage of low or any viscosity fluid along the drive shaft, but without any significant radial load being applied to the sealing sleeve that might cause undue wear or damage due to galling. Moreover, the viscous seal can be manufactured easily and inexpensively. 
   According to the present invention, a compliant viscous seal for a drive shaft comprises an outer body having a shaft hole for passage therethrough of drive shaft to be sealed by the viscous seal, and a sealing sleeve extending axially in the hole and having an inner surface closely surrounding the shaft to effect light contact therewith such that the sealing sleeve can track any angular shifting or radial translating movement of the drive shaft. The inner surface has formed therein a helical groove for preventing leakage of fluid along the shaft when the shaft is rotated within the sealing sleeve. An annular gap is provided between coextensive axial portions of the outer body and sealing sleeve to permit limited pivotal movement of the sealing sleeve relative to the outer body for allowing the sealing sleeve to coaxially align with the shaft when in use, and an annular seal is provided both to seal the annular gap thereby to prevent leakage around the outside of the sealing sleeve and to support the sealing sleeve within the outer body while allowing the sealing sleeve to pivot with a gimbal action within the outer body. 
   The annular seal preferably is flexible and most preferably is resilient. The annular seal can be radially interposed between the sealing sleeve and outer body. In particular, the annular seal, such as an O-ring, can be retained in an annular groove formed in one of the outer body and sealing sleeve, and most preferably in the sealing sleeve. The portion of the annular gap in the region of the resilient annular seal can have a radial dimension less than the radial dimension more remote from the resilient annular seal for more effective sealing of the gap. 
   Further in accordance with the invention, an anti-rotation device is provided to inhibit rotation of the annular seal relative to the outer body while allowing the sealing sleeve to pivot with a gimbal action within the outer body. The anti-rotation device preferably includes one or more keys and slots. For example, aligned slots can be formed in the inner surface of the hole and an outer surface of the sealing sleeve, and a key can be disposed in the radially aligned slots to prevent rotation of the sealing sleeve relative to the outer body, while still permitting the aforesaid pivoting movement. 
   The outer body of the viscous seal can be formed by an outer annular sleeve that can be attached to the housing of the fluid transfer device. In another configuration, the outer body can be unitary with the housing of the fluid transfer device. 
   The compliant viscous seal of the invention generally can be used in any fluid transfer device and has particular application in a gear pump. 
   Further features of the present invention will become apparent to those skilled in the art upon reviewing the following specification and attached drawings. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
       FIG. 1  is an exploded view of a fluid transfer device showing a compliant viscous seal according to the present invention in relation to a cover plate forming part of the fluid containment housing of the fluid transfer device. 
       FIG. 2  is an inner view of the cover plate and compliant viscous seal of  FIG. 1 , with a drive shaft extending through the compliant viscous seal. 
       FIG. 3  is an enlarged fragmentary cross-sectional view taken along the line  3 - 3  of  FIG. 2 , with the drive shaft removed. 
       FIG. 4  is an enlarged inner axial portion of  FIG. 3 . 
       FIG. 5  is an exploded view of another embodiment of a compliant viscous seal according to the present invention, configured for mounting to a housing of a fluid transfer device. 
       FIG. 6  is an outer view the compliant viscous seal of  FIG. 5 . 
       FIG. 7  is a cross-sectional view taken substantially along the lines  8 - 8  of  FIG. 6 . 
   

   DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
   Referring now in detail to the drawings and initially to  FIGS. 1 and 2 , a fluid transfer device is indicated generally at  10 . The fluid transfer device  10  may be of any design aside from the provision of a compliant viscous seal according the present invention, an exemplary embodiment of which is indicated generally at  12 . Consequently, there is shown only the part of the housing  14  of the fluid transfer device through which a drive shaft  16  extends. As illustrated, such housing part is a cover plate  18 . As will be appreciated by those skilled in the art, the fluid transfer device will include other components for carrying out its particular function, be it a fluid pump, fluid motor, etc. In addition, the housing will contain a fluid whose leakage along the drive shaft is stopped by the compliant viscous seal  12 . Although not shown, one or more packing or lip seals can be provided outwardly of the compliant viscous seal, as deemed necessary, to provide a static, fluid tight seal between the drive shaft and the outer body. 
   The compliant viscous seal  12  for the drive shaft  16  comprises an outer body  20  having a shaft hole  22  for passage therethrough of the drive shaft  16 , and a sealing sleeve  24  extending axially in the hole  22 . In the illustrated embodiment, the outer body  20  is formed by an outer sleeve that if fixed, as by press-fitting, in a through bore in the cover plate  18  of the housing  14 . The outer body can be otherwise configured and secured to the housing, or the outer body can be unitary (formed as one piece) with the cover plate or other part of the housing, as may be desired for different applications. 
   The sealing sleeve  24  has an inner surface  30  closely surrounding the drive shaft  16 , preferably with a snug fit such that there is essentially no or a minute clearance between the inner surface  30  and corresponding outer surface of the drive shaft. The inner surface  30  has formed therein one or more helical grooves  32  for preventing leakage of fluid along the drive shaft  16  when the drive shaft is rotated within the sealing sleeve. Rotation of the drive shaft within the sealing sleeve provides a motive force to any leakage fluid, causing the fluid to be reversely pumped back toward the interior of the housing  14  by virtue of the oppositely turned helical groove or grooves  32 , as is well known in the art. That is, the helical groove or grooves have an opposite or reverse “hand” or flight direction as the rotation of drive shaft, such that when drive shaft rotates, the groove or grooves “pump” any fluid leaking down along drive shaft back toward the interior of the housing. The herein reference to a helical groove, unless otherwise indicated, is intended to encompass any known and future equivalents that perform substantially the same function as the helical groove. 
   While the inner generally cylindrical surface  30  of the sealing sleeve  24  can be of a conventional configuration, the outer surface  34  of the sealing sleeve is uniquely configured in relation to the inner surface of the outer body  20 . As best seen in  FIGS. 3 and 4 , the outer, preferably cylindrical, surface  34  of the sealing sleeve is smaller in dimension (diameter) than the inner, preferably cylindrical, surface  36  of the outer body, thereby to provide an annular radial gap  38  between coextensive axial portions of the outer body and sealing sleeve. This gap permits limited pivotal and/or radial translational movement of the sealing sleeve relative to the outer body for allowing the sealing sleeve to coaxially align with the shaft  16  when in use. If, for example, the drive shaft is out of axial alignment with the hole  22  in the outer body, the sealing sleeve can pivot and/or radially shift relative to the outer body to align axially with the drive shaft and/or maintain its axial alignment with the drive shaft, as described in more detail below. 
   As seen in  FIGS. 3 and 4 , a resilient annular seal  40  is interposed between the sealing sleeve  24  and outer body  20  to seal the annular gap  38  thereby to prevent leakage around the outside of the sealing sleeve. The resilient annular seal also performs a second function, this being to support the sealing sleeve within the outer body while allowing the sealing sleeve to pivot with a gimbal action within the outer body and/or to shift radially (translate) relative to the outer body. This gimbal and/or shifting action allows the sealing sleeve to align axially with the drive shaft with little force being exerted on the sealing sleeve. As a result, the sealing sleeve will carry only a nominal radial load that will not cause undue wear or galling. Of course, suitable materials should be selected to withstand this nominal radial load. Such materials can be conventional tool steels for the outer body and sealing sleeve, and conventional resilient materials for the annular seal. By way of further example, the outer body and/or sealing sleeve can be formed of a material (e.g., steel or bronze) appropriate for the particular application. Alternatively, such components could be formed of a non-metal, such as a carbon, silicon carbide, ceramic or plastic. In applications where operating temperatures vary over a wide range, it is best that the sealing sleeve and shaft, in particular, be made of materials having similar coefficients of thermal expansion. 
   The resilient annular seal  40 , such as an elastomeric O-ring, preferably is retained in an annular groove  42  formed in one of the outer body  20  and sealing sleeve  24 , and most preferably in the sealing sleeve as shown. The portion of the annular gap  38  in the region of the resilient annular seal can have a radial dimension less than the radial dimension more remote from the resilient annular seal for more effective sealing of the gap. That is, a conventional O-ring clearance gap, such as about 0.002-0.004 inch on the radius, can be provided in the region surrounding the O-ring and the groove therefor, while a larger radial gap, such as about 0.0125 to 0.015 inch on the radius, can be provided elsewhere to accommodate the desired range of movement of the sealing sleeve relative to the outer body. The O-ring  40  functions as a gimbal support for the sealing sleeve and its resilience also permits radial shifting of the sealing sleeve within the hole in the outer body. Preferably, the sealing sleeve is axially constrained in the outer body by any suitable means, for example to prevent internal fluid pressure from axially forcing the sealing sleeve out of the hole in the outer body. Such constraint could be provided by other parts which radially overlap one or both axial ends of the hole in the outer body. 
   As will be appreciated by those skilled in the art, other annular seal devices can be used to seal and support the sealing sleeve  24 . Such devices can be internal to the housing  14  of the source of fluid leakage as shown, or it can be attached externally to the housing. For example, a radially extending flange can be provided on the sealing sleeve, and an O-ring or gasket can be applied to the flange, on one or both sides. The flange itself can be polished in order to provide a seal, and the flange or the sealing sleeve itself can be made thin enough in construction to provide a flexible seal that allows angular misalignment to be accommodated, merely by flexing the material of the flange or sleeve. The invention is intended to encompass these and other equivalent mounting configurations. 
   Further in accordance with the invention, an anti-rotation device  48  is provided to inhibit rotation of the sealing sleeve  24  relative to the outer body  20  while allowing the sealing sleeve to pivot with a gimbal action and/or radially translate within the outer body. The anti-rotation device preferably includes one or more keys and slots. For example, aligned slots  50  and  52  can be formed respectively in the inner surface of the hole  22  and an outer surface  34  of the sealing sleeve, and a key  54  can be disposed in the radially aligned slots to prevent rotation of the sealing sleeve relative to the outer body, while still permitting the aforesaid pivoting and/or translating movement. The keys, which can be in the form of pins, can be circumferentially equally spaced around the axis of the sealing sleeve. A suitable retention means can be provided for axially retaining the pins in the slots. 
   Referring now to  FIGS. 5-7 , another embodiment of a compliant viscous seal according the invention is disclosed, such be indicated generally at  58 . The seal is in substantial part identical to the seal of  FIGS. 1-4 , and thus like reference numerals are used to denote like parts. The only difference is that the outer body  60  is formed by a circular housing configured for external mounting to a housing of a fluid transfer device  10 . To this end the circular seal housing has a plurality of bores  62  for accommodating bolts used to attach the seal housing to the housing of the fluid transfer device  10  and thus close an opening in the housing through which the drive shaft  16  of the device extends. 
   The compliant viscous seal  12  of the invention generally can be used in any fluid transfer device  10  and has particular application in a gear pump. By way of further example, the fluid transfer device could be a pump for melted synthetic fiber, an extrusion pump, a petroleum distillate pump, a hot melt adhesive pump, etc. The device also can be operated as a pump or motor, depending on whether the shaft is being used to move fluid, or the fluid is being used to move the shaft. 
   The principles, preferred embodiments and modes of operation of the present invention have been described in the foregoing specification. The invention which is intended to be protected herein should not, however, be construed as limited to the particular form described as it is to be regarded as illustrative rather than restrictive. Variations and changes may be made by those skilled in the art without departing from the scope and spirit of the invention as set forth in the appended claims.

Technology Classification (CPC): 5