Abstract:
An alignment apparatus includes a first stator, located in a stator of a piece of rotating equipment, and a second stator couplingly connected to the first stator and able to be angularly rotated relative to the first stator. The second stator can seal an interface between a shaft and housing in the piece of rotating equipment. The alignment apparatus permits angular misalignment between a stator, a housing and a rotor shaft, and may be used, for example, in a bearing protector or an isolator installed on a Pillow Box.

Description:
FIELD OF THE INVENTION 
       [0001]    This invention relates to bearing protectors, both contacting mechanical face seal and Lip Seal type and non-contacting labyrinth seal type and their use in rotating equipment, especially devices, which can accommodate angular rotor to stator misalignment. 
         [0002]    An example of a piece of rotating equipment which is designed to accommodate angular misalignment between the rotating shaft and stator housing is a Pillow Block, occasionally this is also referred as a Plummer Block. Pillow blocks contain a bearing, typically a spherical roller bearing, which is lubricated and sealed between the rotor to stator interface to prevent the ingress or egress of a fluid or solid to a cavity, which results in deterioration of equipment life. 
         [0003]    Bearing protectors are often also referred to as bearing seals or bearing isolators, however, the use of such rotary seals extends well beyond the protection of a bearing in rotating equipment. Accordingly, while reference will be made below to bearing protectors, it should be understood that this term is used, as far as the invention is concerned, in connection with such having wider uses. 
       BACKGROUND TO THE INVENTION 
       [0004]    The purpose of a bearing protector is to prevent the ingress of fluid, solids and/or debris from entering a bearing chamber. Equally, bearing protectors are employed to prevent the egress of fluid or solids from a bearing chamber. Essentially, their purpose is to prevent the premature failure of the bearing. 
         [0005]    Bearing protectors generally fall into two main categories: contacting or non-contacting. 
         [0006]    Non-contacting bearing protectors can be of repeller or labyrinth configuration. Reference is made to our co-pending labyrinth seal bearing protection application GB0415548.7 which defines a substantially non-contacting bearing protector with static shut off device. 
         [0007]    In a non-contacting bearing protector, the rotating component typically has a complex outer profile which is located adjacent and in close radial and axial proximity to a complex inner profile of the stationary component. Together these complex profiles, in theory, provide a tortuous path preventing the passage of the unwanted materials or fluids. 
         [0008]    Conventional labyrinth seal technology indicates the said close radial counter rotational members are substantially parallel to each other and run parallel to the centreline of the shaft. Unfortunately, labyrinth seal technology has limited effectiveness at discouraging fluid, specifically in applications such as Pillow Blocks where angular displacement is expected between the shaft and the housing. 
         [0009]    Contacting bearing protectors can be as basic as a lip seal, or more technical such as a face/mechanical seal. Reference is also made to our co-pending mechanical seal bearing protection application GB0215750.1, which defines a substantially contacting bearing protector with an axially floating seal face against axially static seal face. 
         [0010]    Conventional mechanical seal technology suggests that the counter rotational seal faces attached to the rotor and stator need to be both flat, substantially parallel to each other, and substantially perpendicular to the shaft axis. 
         [0011]    Again, unfortunately, said substantially parallel and perpendicular surfaces have limited effectiveness at sealing fluid, in applications such as Pillow Blocks where angular displacement is expected between the shaft and the housing. 
         [0012]    Pillow Blocks are commonly employed in all types of industries, as they have the advantage of being able to accommodate angular misalignment of the installed equipment. Pillow blocks typically contain one or more centrally disposed bearings contained within a split housing. Two or more said bearing(s) and Pillow Block assemblies are employed to support a longitudinal and substantially rotatable shaft. It is preferable, that the bearing is lubricated during operation, therefore a seal is required, at either side of each split Pillow Block housing, to seal the bearing lubricant. As the two Pillow Blocks are axially spaced, the respective radial distance between the two can often vary from the ideal alignment. It is this radial distance variation that results in a shaft misalignment situation. 
         [0013]    It is therefore deemed advantageous if a mechanism is created which permits both contacting and non-contacting bearing protector types to accommodate angular shaft to housing misalignment whilst permitting the effective sealing of the bearing lubricant fluid. 
         [0014]    Several attempts have made to satisfy this basic sealing requirement, from Schickling U.S. Pat. No. 3,971,565, Lampart U.S. Pat. No. 5,655,845 and Orlowski, U.S. Pat. No. 5,335,921 and WO 98/02669. 
         [0015]    Orlowski U.S. Pat. No. 5,335,921, teaches a two elastomeric members located either side of a projection from a carrier, and frictionally fitted to the sides of the split pillar block. Orlowski relies on the relative elasticity of said elastomer members to accommodate angular misalignment between the carrier and pillar block housing. 
         [0016]    Orlowski, further uses frictional wear rings connected from the carrier to the shaft to force the stationary carrier to align to the rotating shaft. 
         [0017]    The experience reader should note several technical drawbacks with Orlowski U.S. Pat. No. 5,335,921, as follows;
       the frictional rings wear between the rotating shaft and stationary carrier. The worn particles dispersed adjacent and into the sealed bearing lubrication fluid. Said contaminates deteriorate the lubrication media leading to premature bearing failure.   as the elastomeric members are resiliently mounted between the carrier and pillar block housing when the equipment is aligned, given a misalignment situation, one of the two elastomeric members will compress over part of its circumference, whilst the compression on the second elastomer is relieved over part of its circumference. Likewise, the compressive forces at the other part of both elastomers circumferences changes. This irregular circumferential compression force is transmitted through to the frictional rings, accelerating the wear.   all frictional contacting members positioned between two counter rotating surfaces wear both the member and often the surface of the rotor/stator. Such frictional rings thus wear grooves in the shaft, leading to expensive equipment refurbishment costs.   the equipment shaft to housing is angularly rotated about the centreline of the bearing. Often double spherical roller/ball bearings are employed in spilt pillar blocks. Said spherical roller bearings angularly rotate about the radius of the bearing race. Any sealing member which does not also rotate about this bearing race radius is thus resisting the angular rotation, leading to further wear, rapid deterioration of both the bearing and the equipment and failure of the equipment.       
 
         [0022]    It is thus deemed to be further advantageous if said angularly accommodating mechanism, adjacent to the sealing member, does not angularly conflict with the natural angular movement of the bearing. 
         [0023]    Furthermore, it is deemed to be advantageous to avoid the use of frictional alignment wear rings particularly adjacent to the sealed bearing lubricant fluid and not to create uneven circumferential forces around the seal member in a misaligned equipment configuration. 
       STATEMENTS OF THE INVENTION 
       [0024]    According to the present invention there is provided a bearing seal device, with an integral self-aligning joint mechanism. Said self-aligning joint mechanism comprises of two stator members, the first connected to the equipment housing and a second adjacent to the rotor member which is connected to the shaft. 
         [0025]    The self-aligning joint mechanism, specifically the interface between the first and second stator members, is designed to coincide on the extrapolated curved arc of the inner most profile of the outer bearing race, of the bearing mounted in the split pillar block, therefore the self-aligning joint of the invention does not angularly conflict with the natural angular movement of the bearing. 
         [0026]    Preferably the first stator member of the spherical joint mechanism is connected to the split pillar block housing by a radial frictional fit from at least elastomeric member mounted in sealable engagement between said stator member and pillar block housing. 
         [0027]    Preferably, the second stator member, of the self-aligning joint mechanism is configured to requirements of the bearing seal; contacting or non-contacting form. 
         [0028]    Preferably, the two stator members from the self aligning joint mechanism have an elastomeric member mounted in sealable engagement between said members. Preferably, said elastomeric member is allowed to slide between two stator surfaces which run substantially parallel to the self aligning joint mechanism interface. 
         [0029]    Preferably, in the non-contacting configuration, a rotor is positioned adjacent to the second stator member. Preferably said rotor is non-contactingly coupled to said second stator, by a radial support member. 
         [0030]    Preferably, in the non-contacting configuration, said radial support member radially contacts the second stator and rotor and is offered in a low friction material, which may either be wearable or durable/non-wearable. If a wearable material is offered, preferably said radial support member is sited out of the fluid media being sealed. 
         [0031]    Preferably, in the non-contacting configuration, said radial support member is axially positioned from the self-aligning joint mechanism, thereby providing an axial leverage feature, thus permitting a smaller given force to move the self-aligning joint interface of the first stator and second stator and any such elastomer frictional resistance from the sliding member sited between. 
         [0032]    Preferably, in the non-contacting configuration, said radial support member and/or adjacent members, are under no irregular circumference stresses, given that at whatever the final spacial position the self-aligning joint, the frictional resistance from the sealing squeeze of the elastomeric member between the first and second stators, is substantially the same. 
         [0033]    Preferably, in the non-contacting configuration, the rotor to second stator radial and/or axial interference is contactingly sealed when the shaft and rotor is idle and at rest and in non-contact when the shaft and rotor is in operation. Preferably, the rotor is rotationally driven and in sealing engagement with the shaft of the rotary equipment. 
         [0034]    Preferably, said first stator has a radially extending cavity, on its inner most radial surface adjacent to the rotor and/or shaft. At the approximate 6 o&#39;clock position, said radial cavity is discontinued with an orifice that communicates with the bearing chamber of the rotating equipment. 
         [0035]    Preferably, said second stator has a radially extending cavity, on its inner most radial surface adjacent to the rotor and/or shaft. At the approximate 6 o&#39;clock position, said radial cavity is discontinued with an orifice that communicates with the bearing chamber of the rotating equipment. 
         [0036]    Preferably, said second stator is configured to accommodate a conventional contacting Lip/Oil seal, which contact said shaft and perform a seal function. 
         [0037]    Preferably, said second stator is configured to accommodate a contacting face/mechanical seal bearing protector, either of single or dual faced construction, by way of example only, as shown in our corresponding GB0215750.1 application. 
         [0038]    Preferably, said second stator is configured to accommodate a conventional non-contacting restriction bush and/or shaft contacting segmented throttle bush. 
     
    
     
       DESCRIPTION OF THE DRAWINGS 
         [0039]    The accompanying drawings are as follows: 
           [0040]      FIG. 1  is a longitudinal cross section view of a pillow block assembly with a prior art labyrinth seal bearing protector 
           [0041]      FIG. 2  is a longitudinal cross section view of a pillow block assembly with two non-contacting labyrinth seals, of the invention; 
           [0042]      FIG. 3  shows an enlarged longitudinal cross section view of a non-contacting labyrinth seal of the of the first embodiment of the invention; 
           [0043]      FIG. 4  corresponds to  FIG. 2  and is a longitudinal cross section view of a pillow block assembly with the shaft angularly misaligned. 
           [0044]      FIG. 5  corresponds to  FIG. 4  and shows a partial longitudinal cross section of the invention, showing the seal in a positive angularly misaligned condition. 
           [0045]      FIG. 6  corresponds to  FIG. 4  and shows a partial longitudinal cross section of the invention, showing the seal in a negative angularly misaligned condition. 
           [0046]      FIG. 7  shows an enlarged longitudinal cross-section view of a contacting face seal of the invention; 
           [0047]      FIG. 8  shows an enlarged longitudinal cross-section view of a contacting Lip seal of the invention; 
       
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
       [0048]    The invention will now be described, by way of examples only, with reference to the accompanying drawings. 
         [0049]    The general principle of rotary seals in accordance with the present invention may be used not only in the case where the shaft is a rotary member and the housing is a stationary member but also the reverse situation, that is to say, in which the shaft is stationary and the housing is rotary. 
         [0050]    Furthermore, the invention may be embodied in both rotary and stationary arrangements, cartridge and component seals with metallic components as well as non-metallic components. 
         [0051]    Referring to  FIG. 1  of the accompanying drawings, there is illustrated, a pillow block assembly  9  shown, by way of example only, with a prior-art bearing protector assembly  10  assumed, but not shown, to seal both axial ends of the pillow block assembly  9   
         [0052]    The Pillow block assembly  9  includes a rotating shaft  12  and a stationary housing  13 . The stationary housing  13  typically contains a bearing  11 , mounted in the radial space between the shaft  12  and housing  13 . 
         [0053]    Clearly, in order to assemble the bearing  11  into the housing  13 , the housing  13  is typically radially split into two halves, which are clamped together with screws (not shown). 
         [0054]    Area “X”, adjacent to the bearing  11  and at one axial end of the prior-art bearing protector assembly  10  typically contain bearing lubrication fluid, yet could also contain solid and/or foreign debris and/or atmosphere. For clarity it will herewith be termed “product substance”, being used to describe the single or mixed medium. 
         [0055]    Area “Y” at the other axial end of the bearing protector assembly  10  could also partially contain fluid, typically sprayed moisture, and/or solids and/or foreign debris and/or atmosphere, however for clarity it will herewith be termed “atmospheric substance” being used to describe the single or mixed medium. 
         [0056]    The prior-art bearing protector assembly  10  includes a rotor member  14 , which is radially and axially adjacent to stator member  15 . 
         [0057]    The stator member  15  is attached as an integral member to a carrier  16  which, extends radially outwards to engage in a radial groove  17  in Pillow Block housing  13 . At either axial side of the carrier  16  are elastomeric members  18  and  19  which together with the wear rings  20  and  21 , reportively allow the carrier to angularly move substantially parallel to the shaft  12  and substantially misalign with respect to the housing  13 . 
         [0058]    The experienced reader will note, that the shaft will angular pivot about point “Z”, which is the point at which the centreline of the bearing  11  coincides with the centreline of the shaft  12 . The reader will note that the angular rotation of the shaft  12 , is typically a function of the radial distance “R1” between the pivot point “Z” and the arc of the inner most surface  22  of the outer most race  23  of the bearing assembly  11 . 
         [0059]    From  FIG. 1 , given the respective position of the radial groove  17  in housing  13  to the shaft pivot point “Z” it is clear that the prior-art bearing protector seal  10  angularly rotates on a different radius “Rs” to that of the bearing “R1”. 
         [0060]    This difference between “Rs” and “R1” creates a competing set of forces, which ultimately accelerate the deterioration of equipment and seal life. 
         [0061]      FIG. 2  is a longitudinal cross section view of a same pillow block assembly  9 , as previously defined in  FIG. 1 , configured with two non-contacting labyrinth seal assemblies  30  and  31 , of the first embodiment of the invention. 
         [0062]    From  FIG. 2 , the non-contacting labyrinth seal assembly  30 , comprises of a rotor  32 , a floating stator  33  and a stator socket  34 . The floating stator  33  is axially and radially seated on the stator socket  34 , about arc  35  thus permitting the floating stator  33  to angularly misalign with respect to the stator socket  34 . 
         [0063]    The centre point of said arc  35 , substantially coincides with the shaft pivot point “Z”. The radius “R2” of arc  35 , is substantially the same “R1” which is arc of the bearing inner most radial surface  22  of the outer most bearing race  23 . 
         [0064]    Since “R1” is the same as “R2”, the angular rotation of both non-contacting labyrinth seal assemblies  30  and  31  is the same as the shaft  12  to housing  13  of the pillow block  9 . As no conflict of annular rotation exists within the Pillow block  9  assembly, both seal life and equipment life is not compromised. 
         [0065]    This self-aligning joint arrangement, between the floating stator  33  and stator socket  34  forms the first embodiment of the invention 
         [0066]      FIG. 3  corresponds to  FIG. 2  and shows an enlarged longitudinal cross section view of a non-contacting labyrinth seal assembly  31  of the invention. 
         [0067]    As previously described, the rotor  42  is adjacent to the floating stator  43 , which is radially and axially seated on the stator socket  44 . Both the floating stator  43  and stator socket  44  are seated on an arc interface  45  with radius of “R2”, which is substantially the same as the shaft pivot radius “R1” from  FIG. 2 . 
         [0068]    The rotor  42  is radially mounted in sealingly engagement with shaft  12  by at least one elastomeric members  46 . The frictional squeeze on said elastomer  46  is typically sufficient to transmit the rotational drive from the shaft  12  to the rotor  42 . Clearly, a separate drive mechanism could be employed to transmit said drive if so required. 
         [0069]    The static shut off device  47 , which seals the rotor to stator when the shaft is at rest and provides a non-contact seal when the shaft is in operation, is defined in our co-pending labyrinth seal bearing protection application GB0415548.7 and will not be further described. Clearly, the present invention may be offered with or without such a static shut off feature or an equivalent. 
         [0070]    The reader will understand that as long as there is a sufficient axial force maintaining the spherical seating relationship between the floating stator  43  and stator socket  44 , a seal could be obtained at said arc interface  45  of the first embodiment. However, given the likelihood of equipment vibration, tolerancing and general uncertainties associated with operating rotating equipment, it is preferable that the second embodiment of the invention, is employed in the assembly, as herewith described. 
         [0071]    On the outer most radial surface of the floating stator  43 , is an elastomeric member  48 . Said elastomeric member is preferably that of a solid deformable toroid, however could equally be that of a hollow deformable toroid or any form of sealing and/or axially engerising configuration. Preferably, any such member  48  should have low coefficient of friction properties. 
         [0072]    Said elastomer  48  is sealingly engaged to the outer circumference of the floating stator  43 . Preferably, said floating stator  43  incorporates at least one radially extending portion, which abuts to said elastomer  48 . 
         [0073]    Preferably, the stator socket  44  incorporates a radially extending surface  50 , preferably an arc form with radius of “R3”, which is substantially parallel to “R2”. 
         [0074]    Given the substantially parallel feature, preferably the radial distance between “R2” and “R3” is constant and of a smaller distance than the cross section of elastomer  48 . This smaller distance between the stator socket  44  and floating stator  43  creates a radial sealing squeeze on the elastomer cross section. Preferably said radial squeeze is between 0.995% and 0.80% of the elastomer  48  cross section. 
         [0075]    The substantially parallel surface  50  of the stator socket  44  to the seating arc  45  between the floating stator  43  and stator socket  44 , with a solid deformable toroid in sealingly engagement in the radial space in-between, defines the second embodiment of the invention. 
         [0076]    The experienced reader will therefore see the advantage of the second embodiment of the invention in that for any given angular rotational displacement of the stator socket  44  to floating stator  43 , elastomer  48  provides a constant, uniform sealing engagement between the two parts  44  and  43 . Said uniform sealing is a result of a uniform force applied to said elastomer  48  which is constant around the circumference of the elastomer  48 . Thus said elastomer  48  does not inflict forces and stresses on other members within the Pillow Block arrangement, which create undesirable effects on seal wear, seal life and equipment life. This means that the floating stator  43 , can be positioned in any angular misalignment condition, and there is no, spring-like force, trying to move to collide with the counter rotating rotator  42 . Furthermore, the frictional resistance of the elastomer  48  with stator socket  44  and floating stator  43  is sufficient to overcome the forces of gravity, acting on the floating stator  43 , thus again preventing contact the rotor  42 . 
         [0077]    The coupled stator assembly  70 , comprising of the floating stator  43  and the socket stator  44 , is axially and radially coupled, yet both parts are permitted to angularly swivel as previously discussed. Clearly, in addition, both parts could also be rotationally coupled, by example only, a drive pin (not shown) in the floating stator  43  operating in a clearance slot (not shown) in the socket stator  44 . 
         [0078]    From  FIG. 3 , the stator socket  44  is radially located in the Pillow block housing  13  and preferably in sealing engagement using one or more elastomeric members  51 . 
         [0079]    The frictional sealing squeeze on said elastomer  51  is typically sufficient to transmit the anti-rotational drive from the housing  13  to the stator socket  44 . Clearly, a separate drive mechanism could be employed to transmit said drive if so required. 
         [0080]    Preferably, as shown, the stator socket  44 , is also axially retained given the width of the radially extending portion on the outer most circumferential part  52 , engages in the radially extending groove of the inner most portion of the housing  13 . 
         [0081]    Clearly, the radial location, axial location and sealing arrangement between the stator socket  44  and housing  13  can be changed to suit a specific application or desired equipment configuration. Clearly, the invention anticipates other such location and sealing engagement of these two members and by way of example only (not shown), the stator socket could incorporate a radially extending flange containing one or more axially extending holes. Said flange could incorporate a sealing member, like a gasket allowing the socket stator to be secured to the Pillow block housing by a bolt located through the flange hole into a corresponding threaded hole in the pillow block. 
         [0082]    Referring back to  FIG. 3 . Non-contacting labyrinth seals rely on a close radial clearance between the rotor  42  and stator  43 , and, where possible, a series of radially and axially extending castellations are incorporated in both counter rotational members, to create a tortuous path of resistance for fluid to pass. 
         [0083]    Preferably, the radial and axial clearances between the rotor  42  and  43  should be kept constant, around the entire circumference of the two parts. Clearly, if the shaft  12  is misaligned to the housing  13 , the rotor  42  will be misaligned to the housing  13 , since the rotor  42  is concentrically mounted to the shaft. During equipment assembly therefore, the rotor will be radially displaced with respect to the floating stator  43 , as a result of angular movement of the shaft  12 . If this radial displacement is larger than the radial clearance between the rotor  42  and floating stator  43 , the floating stator  43  radially follows the rotor  42  effortlessly until the final running position is reached. The effortless movement of the floating stator  43  is due to the axial location of the rotor  42  with respect to the arc seat  45  of the floating stator and the resulting leverage advantages to overcome the slight frictional resistance of the assembly. 
         [0084]    Clearly, as both rotor  42  and stator  43  parts are typically made from a wearing material, such as phosphor bronze, any slight and brief contact between the two, during equipment start-up, is typically acceptable. The point to note is that since there is no “spring like” forces, acting on the floating stator to maintain said counter-rotational contact, the contact is brief—typically that of a split second, thereafter, returning to a non-contact operation. 
         [0085]    The third embodiment of the invention however, offers an additional feature, if required, to eliminate any such contact between the rotor  42  and floating stator  43 . 
         [0086]    From  FIG. 3 , the rotor  42  has a radially extending groove  60  which houses an alignment shield  61 . The inner most radial feature of said alignment shield  61  is in close radial proximity to the outer most circumference of the floating stator  43 . 
         [0087]    Preferably, the alignment shield  61 , is manufactured from a material with poor wear resistance and low co-efficient of friction, typically a plastic such as Teflon or a Teflon derivative. Teflon is a trade name of Dupont. 
         [0088]    Said alignment shield  61  sets a constant radial clearance around the circumference of the rotor  42  and stator  43 , therefore ensuring that if the rotor  42  radially displaces given angular shaft  12  movement, the floating stator  43 , radially follows the rotor  42 . Any start-up contact, remains slight and brief but is now made between the sacrificial alignment shield  61  and floating stator  43 . 
         [0089]    Furthermore, the sacrificial alignment shield  61  is out of contact with the sealed bearing fluid/lubrication at position “X” in  FIG. 3 . Therefore, unlike the prior-art designs, specifically the wear rings, item  24  of Orlowski U.S. Pat. No. 5,335,921, any debris from such counter-rotational contact can not contaminate the bearing fluid or add heat to in, which can lead to the breakdown of the lubricant properties. 
         [0090]    The experienced reader will relate to the clear advantage of such a third embodiment, particularly the leverage advantage given the axial distance between the alignment shield  61  and seat interface  45 . However, the added benefit of the alignment shield  61  is that it aids the axial unitisation the rotor  42  and floating stator  43  for assembly/disassembly onto the shaft, whilst protecting against moisture entering the radial gap  63  adjacent to said alignment shield  61 . 
         [0091]    From  FIG. 3 , the floating stator  43  has an outboard orifice  67 , positioned at the 6 o&#39;clock position when viewing the assembly. This orifice  69  facilitates the drainage of any moisture that migrations past the alignment shield  61  into the radial gap  63 . However, from  FIG. 3 , the fourth embodiment of the invention is also apparent, which relates to the unique orifice feature  68  and  69  adjacent to the bearing fluid/lubrication “X”. 
         [0092]    The socket stator  44  includes a radially extending velocity reducing cavity  71 . As bearing fluid enters said circumferential cavity  71 , typically in the form of splash droplets generated from the bearing&#39;s rotation, the bearing fluids velocity changes allowing gravity to move said fluid around the circumference of the cavity to the 6 o clock position. The socket stator  44  has at least one orifice, positioned at the 6 o&#39;clock position, which communicates from the velocity reducing cavity  71  to the bearing cavity “x”. This communication orifice permits bearing fluid to be drained away from said cavity  71 , back to the bearing cavity. 
         [0093]    A second velocity reducing cavity  72  is formed between the radially extending seat arc surface  45  of the floating stator  43  and the radially extending feature  65  of the inner most surface of the socket stator  44 . Again, an orifice  66 , sited at the 6 o&#39;clock position, communicates from said cavity  65  to said cavity  71 . 
         [0094]    A third velocity reducing cavity is formed by a radially extending cavity  73  on the inner most surface in the floating stator  43 , with an orifice  68 , communicating from said cavity  73  to said cavity  72   
         [0095]    The fourth embodiment of the invention thereby discloses an unique and highly effective velocity reducing series contained within a coupled stator assembly. Said velocity reducing series comprises of two or more, velocity reducing cavities formed between the shaft  12  and the coupled stator assembly  70 . Said velocity reducing cavities are connected by two or more communication orifices, preferably in line with one another and position at the 6 o&#39;clock position in the coupled stator assembly, thus permitting bearing fluid/lubrication to drain back to the bearing chamber of an item of rotating equipment. 
         [0096]      FIG. 4  corresponds to  FIG. 2  and is a longitudinal cross section view of a pillow block assembly  80  containing a bearing assembly  81  and two non-contacting labyrinth seal assemblies  82  and  83  of the invention. 
         [0097]      FIG. 4  shows the shaft  12  with shaft axis  84  angularly misaligned with respect to the bearing housing  13  with bearing housing axis  85 , through angle “B”. Typically, angle B can be engineered to be anything the application demands, but typically it ranges from 0 degrees to 5 degrees. 
         [0098]    As shown in  FIG. 4 , the coupled stator assemblies  86  and  87  accommodate said angular misalignment, specifically sealing elastomers  88  and  89  remain in sealingly contact with their respective coupled stator sealing surfaces. 
         [0099]      FIG. 6  corresponds to  FIG. 4  and shows a partial longitudinal cross section of the invention, showing an enlarged view of the non-contacting labyrinth seal  83  in a positive (radially upwards) angular shaft mis-aligned condition. 
         [0100]      FIG. 6  corresponds to  FIG. 4  and shows a partial longitudinal cross section of the invention, showing an enlarged view of the non-contacting labyrinth seal  83  in a negative (radially downwards) angular mis-aligned condition. 
         [0101]      FIG. 7  shows an enlarged partial longitudinal cross-section view of the fifth embodiment of the invention, illustrating the coupled stator assembly  90 , specifically the floating stator  91  adapted to house a contacting face seal assembly ( 92 ), as substantially disclosed, but not limited to, the invention of our co-pending GB0215750.1 application. 
         [0102]      FIG. 8  shows an enlarged partial longitudinal cross-section view of the sixth embodiment of the invention, illustrating the coupled stator assembly  100 , specifically the floating stator  101  adapted to house a contacting Lip seal ( 102 ). 
         [0103]    The six embodiments of the invention, described and shown, clearly show innovative step and considerable advantages, over the existing prior art sealing, of rotating equipment, such as pillow blocks, which, by their nature, create angular shaft to housing misalignment.