Shaft seal assembly

Abstract

To provide a sealed shaft seal assembly that, in combination with a pressurized sealing fluid, is capable of preventing both product and contaminants from contacting the interior of the shaft seal assembly.SOLUTION: An illustrative embodiment of a shaft seal assembly generally includes a first stator, a second stator, and a throttle member. In one illustrative embodiment, the second stator may be formed with a main body and an access plate disposed radially interior with respect to a portion of the first stator. The first stator and second stator may engage one another about a semi-spherical interface in which the semi-spherical interface is comprised of a convex surface on the second stator and a concave surface on the first stator. The second stator may include an internal channel in which a throttle member may be disposed, and a radially-interior surface of the throttle member may be disposed adjacently to a shaft.SELECTED DRAWING: Figure 20B

Description

[Technical field]

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS This application claims priority to U.S. Provisional Patent Application No. 62 / 738,797, filed September 28, 2018. [Background technology]

[0002] FIELD OF THE DISCLOSURE The present invention relates to a shaft seal assembly having a number of embodiments. In some embodiments, the shaft seal assembly may be used as a product seal between a product container and a shaft therein. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] U.S. Patent No. 7,090,403 Summary of the Invention

[0004] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments and, together with the description, serve to explain the principles of the apparatus and method. The drawings illustrate exemplary embodiments only and are therefore not to be considered as a limitation on the scope of the invention, which apparatus and method will be described and explained with further specificity and detail through the use of the accompanying drawings. [Brief description of the drawings]

[0005] [Figure 1] FIG. 2 is an outer perspective view of the shaft seal assembly; [Diagram 2] FIG. 2 is an outer end view of the shaft seal assembly with the shaft elements aligned; [Diagram 3] 3 is a cross-sectional view of the first embodiment of the shaft seal assembly shown in FIG. 2 assembled to a housing. [Figure 3A] FIG. 11 is a diagram of the first surface seal-shaft integration while the shaft is being angularly and radially aligned. [Figure 3B]FIG. 11 is a diagram of the second surface seal-shaft integration while the shaft is being angularly and radially aligned. [Figure 4] FIG. 13 is an exterior end view with shaft misalignment. [Diagram 5] FIG. 4 is a cross-sectional view of the first embodiment shown in FIG. 3 with misalignment applied both angularly and radially of the shaft. [Figure 5A] FIG. 11 is a diagram of the first seal-shaft integration enabled by interlocking while the shaft is both angularly and radially misaligned. [Figure 5B] FIG. 13 is a diagram of a second seal-shaft integration enabled by interlocking while the shaft is both angularly and radially misaligned. [Figure 6] FIG. 3 is a cross-sectional view of a second embodiment of the shaft seal assembly shown in FIG. 2. [Figure 7] FIG. 3 is a cross-sectional view of the third embodiment shown in FIG. [Figure 8] FIG. 13 is a perspective view of the fourth embodiment assembled to a vessel wall. [Figure 9] FIG. 1 is a cross-sectional view of a first embodiment of a shaft seal assembly pressure balanced and assembled to a housing with the shaft in an aligned position. [Figure 9A] FIG. 1 is a detailed view of a portion of the first embodiment of the shaft seal assembly adjacent the vent port with the pressure balanced and the shaft aligned; [Figure 9B] FIG. 1 is a detailed view of a portion of the first embodiment of the shaft seal assembly adjacent the fluid return with the pressure balanced and the shaft in an aligned position. [Figure 10] FIG. 2 is a cross-sectional view of a first embodiment of a pressure balanced shaft seal assembly shown during shaft misalignment. [Figure 10A] FIG. 13 is a detailed view of a portion of the first embodiment of the shaft seal assembly adjacent the vent port with the pressure balanced and the shaft in a misaligned state. [Figure 10B] FIG. 1 is a detailed view of a portion of the first embodiment of the shaft seal assembly adjacent the fluid return with the pressure balanced and the shaft in a misaligned condition. [Figure 11]FIG. 13 is a cross-sectional view of a second embodiment of a pressure balanced shaft seal assembly with the shaft in an aligned position; [Figure 12] FIG. 13 is a cross-sectional view of a third embodiment of a pressure balanced shaft seal assembly with the shaft in an aligned state; [Figure 13] 1 is a cross-sectional view of another embodiment of a bearing separator (or shaft seal assembly) configured with a rotor. [Figure 14] 13 is a cross-sectional view of a portion of yet another embodiment of a bearing separator (or shaft seal assembly) configured with a rotor. [Figure 14A] 15 is a cross-sectional view of a portion of the embodiment of the bearing separator shown in FIG. 14 with the shaft misaligned and / or radially displaced. [Figure 15] 14 is a partial cross-sectional view of the embodiment of the bearing separator shown in FIG. 13 with the shaft misaligned and / or radially displaced. [Figure 15A] FIG. 16 is a detailed view of a portion of the bearing separator embodiment shown in FIG. [Figure 16A] FIG. 2 is an exterior view of an exemplary embodiment of a multi-hole shaft seal assembly, with some hidden surfaces shown in dashed lines; [Figure 16B] FIG. 16B is a cross-sectional view of an embodiment of a multi-hole shaft seal assembly taken along line AA shown in FIG. 16A. [Figure 17A] FIG. 2 is an exterior view of one embodiment of a sealing member that may be used with various embodiments of a multi-hole shaft seal assembly. [Figure 17B] 17B is a cross-sectional view of the embodiment of the sealing member shown in FIG. 17A taken along line KK. [Figure 18] FIG. 13 is a top front view of another exemplary embodiment of a shaft seal assembly; [Figure 18A] FIG. 20 is a cross-sectional view of the exemplary embodiment of the shaft seal assembly of FIG. 18 taken along line AA. [Figure 18B] FIG. 20 is a cross-sectional view of the exemplary embodiment of the shaft seal assembly of FIG. 18 taken along line BB. [Figure 18C] FIG. 20 is a cross-sectional view of the exemplary embodiment of the shaft seal assembly of FIG. 18 taken along line CC. [Figure 19]FIG. 18 is a perspective view of the shaft seal assembly shown in FIGS. 18 to 18C. [Figure 19A] FIG. 20 is a perspective cross-sectional view of the shaft seal assembly shown in FIGS. 18 and 19. [Figure 19B] FIG. 2 is a side exploded view of the shaft seal assembly shown in FIGS. 18 to 19A. [Figure 19C] FIG. 20 is a perspective exploded view of the shaft seal assembly shown in FIGS. 18-19B, with the inner side in the foreground. [Figure 19D] FIG. 19C is another perspective exploded view of the shaft seal assembly shown in FIGS. 18-19C with the outer side in the foreground. [Figure 20A] FIG. 13 is a top elevational view of another exemplary embodiment of an illustrated shaft seal assembly; [Figure 20B] FIG. 20B is a perspective view of an exemplary embodiment of the shaft seal assembly shown in FIG. 20A. [Figure 21A] FIG. 2 is a perspective exploded view of another exemplary embodiment of a shaft seal assembly with an outer side in the foreground; [Figure 21B] FIG. 21B is a cross-sectional view of the exemplary embodiment of the shaft seal assembly shown in FIG. 21A along the longitudinal axis of a shaft, the shaft engaged with the shaft seal assembly. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0006] Before the present methods and apparatus are disclosed and described, it is not intended that the methods and apparatus be limited to particular methods, components, or implementations. The terminology used herein is for the purpose of describing particular embodiments / aspects only and is not intended to be limiting.

[0007] As used in this specification and the appended claims, the singular forms "a," "an," and "the" include plural referents unless the context clearly dictates otherwise. As used herein, ranges can be expressed as from "about" one particular value, and / or to "about" another particular value. When such a range is expressed, another embodiment includes from the one particular value and / or to the other particular value. Similarly, when values ​​are expressed as approximations, the particular value forms another embodiment by use of the antecedent "about." Each endpoint of a range is significant in relation to the other endpoint, and independently of the other endpoint.

[0008] "Optional" or "optionally" means that the event or circumstance described below may or may not occur, and that the description includes cases where the event or circumstance occurs as well as cases where the event or circumstance does not occur.

[0009] "Aspects," when referring to a method, apparatus, and / or apparatus components, do not imply that a limitation, feature, component, etc., is required to be referred to as an aspect, but rather that the aspect is part of a particular exemplary disclosure and does not limit the scope of the method, apparatus, and / or apparatus components unless so indicated in the claims below.

[0010] Throughout the description and claims of this specification, the term "comprise" and variations of the term "comprise", such as "comprising" and "comprises", mean "including, but not limited to", and are not intended to exclude, for example, other components, integers, or steps. "Exemplary" means "one example of" and is not intended to convey an indication of a preferred or ideal embodiment. "Etc." is used for descriptive purposes rather than in a limiting sense.

[0011] Disclosed are components that can be used to implement the disclosed methods and apparatus. When these and other components are disclosed herein, combinations, subsets, interactions, groups, etc. of these components are disclosed, while specific references to each and every individual various collective combinations and permutations thereof may not be explicitly disclosed, but each is specifically contemplated and described herein for all methods and apparatuses. This applies to all aspects of this application, including, but not limited to, the steps of the disclosed methods. Thus, if there are various additional steps that can be implemented, each of these additional steps can be implemented with any particular embodiment or combination of embodiments of the disclosed methods.

[0012] The present methods and apparatus may be more readily understood by reference to the following detailed description of the preferred embodiments and examples contained herein, the drawings, the previous description, and the following description, in which corresponding terms may be used interchangeably when referring to generalities of configurations and / or corresponding components, aspects, features, functions, methods and / or materials of construction, etc.

[0013] The disclosure is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the drawings. The disclosure is capable of other embodiments and can be practiced or carried out in various ways. Additionally, the phraseology and terminology used herein relating to the orientation of devices or elements (e.g., terms such as "front", "back", "up", "down", "top", "bottom", etc.) are used for simplicity of description only and are not intended to indicate or imply that the device or element referred to must have only a particular orientation. Furthermore, terms such as "first", "second" and "third" are used herein and in the appended claims for descriptive purposes and are not intended to indicate or imply any relative importance or significance. Additionally, any dimensions recited or read in the present invention are for illustrative purposes only and are in no way meant to limit the scope of the present disclosure unless so recited in the claims.

[0014] 1-5 provide various views of a first exemplary embodiment of a shaft seal assembly 25 that allows sealing of various lubricating fluids within a bearing housing 30 and / or preventing ingress of contaminants into the housing 30, which may be configured as a bearing housing. FIGS. 6 and 7 provide an alternative exemplary embodiment of the shaft seal assembly 25 in which a sealing fluid is used. Applicant defines the sealing fluid to include at least both liquid and vapor. Applicant considers air, nitrogen, water and water vapor, as well as any other fluid within the spirit of the present disclosure, any other fluid may work with the proposed shaft seal assembly to provide a pressurized fluid barrier for any and all embodiments disclosed within the scope of the present disclosure. The gas or fluid selected may be based at least on process compatibility with the product being sealed.

[0015] 1 is an exterior perspective view of a first exemplary embodiment of a shaft seal assembly 25, where the shaft seal assembly 25 is placed with and engaged with a shaft 1, which is inserted through a stationary stator 2 of the shaft seal assembly 25. FIG. 2 is an exterior end view of the shaft seal assembly 25, where the shaft 1 is aligned within the shaft seal assembly 25.

[0016] FIG. 3 is a cross-sectional view of a first embodiment of the shaft seal assembly 25 shown in FIG. 2, illustrating that the shaft seal assembly 25 may be configured as a labyrinth seal to retain lubricating fluid within the bearing cavity 32 of the housing 30 and / or prevent ingress of contaminants into the housing 30. The shaft 1 shown in FIG. 3 may undergo multiple radial, angular or axial movements relative to the stationary stator 2 or a portion of the stationary stator 2. The stationary stator 2 of the shaft seal assembly 25 may engage the housing 30 via any suitable method and / or structure including, but not limited to, flange mounting or press fit. The shaft seal assembly 25 may also be used in applications involving a rotating housing and a stationary shaft (not shown). The shaft 1 may be free to move axially relative to the shaft seal assembly 25 if the particular application of the shaft 1 and / or shaft seal assembly 25 requires.

[0017] A labyrinth seal 3 having an inner surface may be located adjacent to the shaft 1. A defined gap 6 may exist between the inner surface of the labyrinth seal 3 and the shaft 1. A rounded surface 3a may be configured such that the surface 3a faces the inner surface of the labyrinth seal 3. The rounded surface 3a of the labyrinth seal 3 and the interior of the floating stator 4 may be configured to form a spherical interface 11. An O-ring passage 15 and an O-ring 7 may be arranged to cooperate with the rounded surface 3a of the labyrinth seal 3 to seal (or confine) fluid movement through, between, and along the engaged labyrinth seal 3 and floating stator 4 while maintaining the spherical interface 11. This spherical interface 11 may enable limited relative rotational movement (engagement) between the labyrinth seal 3 and the floating stator 4.

[0018] The illustrated O-ring passage 15 can be machined into the floating stator 4 and located at the spherical interface 11 with the labyrinth seal 3. The O-ring passage 15 can be configured to be annular and continuous with the labyrinth seal 3. The O-ring passage 15 and O-ring 7 can also be located within the labyrinth seal 3 adjacent to the spherical interface 11. In some embodiments, the O-ring 7 can be constructed from a material that is compatible with both the product being sealed and the preferred sealing fluid. However, the O-ring passage 15 and O-ring 7 are one possible combination of structures that can be used to seal the various parts within the shaft seal assembly 25. Any other structures and / or methods for a particular embodiment of the shaft seal assembly 25 can be used without limitation.

[0019] The advantageously located anti-rotation pin(s) 12 may be inserted into the anti-rotation groove 10 and serve to limit relative rotational motion between the labyrinth seal 3 and the floating stator 4. The multiple anti-rotation grooves 10 and pins 12 may be located about a radius of the shaft 1. When the shaft seal assembly 25 is used in combination with a sealing fluid, the advantageous anti-rotation pin 12 may be eliminated, allowing the corresponding anti-rotation groove 10 to serve as a flow passage through the vent 9 and lubricant return 5, one exemplary embodiment of which is shown in FIG. 7. Furthermore, the diametric relationship of the anti-rotation pin 12 and anti-rotation groove 10, respectively, may be selected to tolerate some angular misalignment of the shaft 1. For example, a relatively small diameter anti-rotation pin 12 may be used with a large diameter anti-rotation groove 10 to allow for greater relative motion of the labyrinth seal 3 with respect to the floating stator 4 in response to angular misalignment of the shaft 1. The labyrinth seal 3 is one possible embodiment of a sealing structure that may be used adjacent the shaft 1 in the shaft seal assembly 25. However, other structures and / or methods may be used to accomplish similar functionality without limitation.

[0020] The annular passage may be formed in the fixed stator 2 and defined by gaps 20 and 21 provided between the exterior of the floating stator 4 and the interior of the fixed stator 2 of the shaft seal assembly 25. The annular passage of the fixed stator 2 is highlighted in FIG. 2 as A-A′. The annular passage of the fixed stator 2 may be formed with an inner surface configured to be substantially perpendicular to the axis 1. An outer surface of the floating stator 4, which may be substantially contained within the annular passage of the fixed stator 2, may cooperatively engage with a first orthogonal inner surface and a second orthogonal inner surface of the fixed stator 2. The inner boundary surface may be formed by a first (inside of the shaft seal assembly 25) orthogonal annular passage surface of the fixed stator 2, which engages with a first (inside) orthogonal surface of the floating stator 4. The outer boundary surface may be formed by a second (outside of the shaft seal assembly 25) orthogonal annular passage surface of the fixed stator 2, which engages with a second (outside) orthogonal surface of the floating stator 4. The O-ring passages 19 and O-rings 13 may be disposed in and cooperate with a surface of the floating stator 4 perpendicular to the axis 1. These O-rings 13 may function to seal (or confine) fluid movement along and between the mating floating stator 4 and fixed stator 2 while allowing for limited relative rotational movement between the floating stator 4 and fixed stator 2. The floating stator 4 and fixed stator 2 are one possible embodiment of cooperating mating portions of the shaft seal assembly 25, which are configured to allow relative movement between the cooperating mating portions in at least one dimension and may be used in combination with the labyrinth seal 3 in the shaft seal assembly 25. However, other structures and / or methods may be used to achieve similar functionality, without limitation.

[0021] The O-ring passage 19 may be annular and configured to be continuous with respect to the shaft 1. In one embodiment not shown, the O-ring passage 19 and the O-ring 13 may be located within the body of the floating stator 4 rather than the fixed stator 2. It is contemplated that in many applications, it may be optimal to locate these O-ring passages 19 and corresponding O-rings 13 in a similar proximate relationship. In some embodiments, the O-ring 7 may be constructed from a material that is compatible with both the product to be sealed and the preferred sealing fluid. However, the O-ring passage 15 and the O-ring 7 are one possible combination of structures that may be used to seal the various parts within the shaft seal assembly 25. Any other structures and / or methods suitable for a particular embodiment of the shaft seal assembly 25 may be used without limitation.

[0022] A strategically placed anti-rotation pin(s) 8 may be inserted into the anti-rotation groove 16 and serve to limit both relative radial and rotational movement between the inside of the floating stator 4 and the fixed stator 2. A number of anti-rotation grooves 16 and pins 8 may be placed around the radius of the shaft 1. The diametric relationship between the anti-rotation pins 8 and the anti-rotation grooves 16 may also be selected to allow for some angular misalignment of the shaft 1. For example, a small diameter anti-rotation pin 8 and a large diameter fixed stator anti-rotation groove may allow for greater relative movement of the labyrinth seal 3 in response to angular misalignment of the shaft 1.

[0023] The labyrinth pattern seal groove 14 may be vented through one or more vents 9 to allow pressure equalization. If desired, the vents 9 may be supplied with pressurized sealing fluid, which overpressurizes the labyrinth region 14 and shaft seal gap 6, increasing the efficiency of the shaft seal assembly 25. The spherical interface 11 between the labyrinth seal 3 and the floating stator 4 may be configured to allow for angular misalignment between the shaft 1 and the fixed stator 2. The O-ring passage 19 is annular with respect to the shaft 1 and may be machined into the fixed stator 2 and located at the interface between the fixed stator 2 and the floating stator 4, as shown. The O-ring passage 19 may also be located within the floating stator 4 and may engage an O-ring 13, which may be configured to provide sealing contact with the fixed stator 2.

[0024] FIG. 3A shows a view of the seal-shaft integration during angular and radial alignment of the shaft 1. This view highlights the alignment of the axial surface 17 of the labyrinth seal 3 with the axial surface 18 of the floating stator 4. In particular, it focuses on the alignment of the axial surfaces 17, 18 between the floating stator 4 and the labyrinth 3 at the spherical interface 11. FIG. 3B shows the shaft-seal integration during angular and radial alignment of the shaft 1 in the opposite plane to that shown in FIG. 3A. This view highlights the alignment of the axial surface 17 of the labyrinth seal 3 with the axial surface 18 of the floating stator 4, respectively, for the opposite portion of the shaft seal assembly 25 shown in FIG. 3A. Those skilled in the art will appreciate that the exemplary embodiment of the shaft 1 and shaft seal assembly 25 are circular in shape, so naturally the surfaces will represent 360 degrees around the shaft 1. Again, particular focus is placed on the alignment of the axial planes 17, 18 between the labyrinth seal 3 and the floating stator 4 at the spherical interface 11. Figures 3A and 3B also show a first defined gap 20 between the floating stator 4 and the fixed stator 2, and a second defined gap 21 between the floating stator 4 and the fixed stator 2, opposite the first defined gap 20.

[0025] 2, 3, 3A and 3B, shaft 1 undergoes no radial, angular or axial movement relative to housing 30. Thus, defined gaps 20 and 21 of this width, which in the exemplary embodiment may be substantially equal, exhibit little movement or misalignment on floating stator 4.

[0026] Figure 4 is an outer end view of the shaft seal assembly 25 with misalignment of the rotatable shaft 1. Figure 5 is a cross-sectional view of the first embodiment of the shaft seal assembly 25 shown in Figure 3 with both angular and radial misalignment of the shaft 1. The shaft 1 shown in Figure 5 is also of a type that may undergo radial, angular or axial movement relative to the fixed stator 2 (and / or housing 30) of the shaft seal assembly 25.

[0027] 5, the radial gap 6 of the labyrinth seal 3 defined relative to the shaft 1 may be maintained despite the change in the shaft misalignment angle 31. The shaft 1 may still be free to move axially despite the change in the shaft misalignment angle 31. The configuration of the shaft seal assembly 25 may allow the labyrinth seal 3 to move with the floating stator 4 as radial movement is introduced to the shaft 1.

[0028] The labyrinth seal 3 and the floating stator 4 may be secured together by one or more compression O-rings 7, or any other suitable structure and / or method. Rotation of the labyrinth seal 3 within the floating stator 4 may be prevented by an anti-rotation member, which may include, but is not limited to, a screw, an anti-rotation pin 8, or a similar device that blocks rotation. The pins shown in Figures 3, 3A, 3B, 5, 6, and 7 are one structure that prevents rotation of the labyrinth seal 3 and the floating stator 4. However, any other suitable structure and / or method may be used without limitation to achieve a similar result.

[0029] Lubricant, sealing fluid or other medium may be collected and discharged through a series of one or more optional exhaust ports or lubricant return paths 5. The labyrinth seal 3 may be pressure equalized by venting through one or more vent ports 9. If desired, the vent ports 9 may be supplied with pressurized air or other gas or fluid medium to overpressurize the labyrinth seal 3 and increase sealing efficiency. The combination of tight tolerances between cooperating mating machine parts of the shaft seal assembly 25 and the pressurized sealing fluid may prevent both product and contaminants from contacting the interior of the shaft seal assembly 25. The spherical interface 11 between the labyrinth seal 3 and the floating stator 4 may be configured to tolerate angular misalignment between the shaft 1 and the fixed stator 2. The O-ring passage 19 and the O-ring 13 that may be disposed within the O-ring passage 19 may cooperate with opposing faces of the floating stator 4, which may be configured substantially perpendicular to the axis of rotation of the shaft 1. In this way, the O-ring 13 cooperates with the floating stator 4 to seal (or confine) fluid movement between and along the floating stator 4 and the labyrinth seal 3, whilst allowing relative radial movement between the stator 4 and the fixed stator 2.

[0030] 5A illustrates the seal-shaft integration enabled by the shaft seal assembly 25 during angular and radial misalignment of the shaft 1. This figure highlights that the offset or interlocking of the axial surface 17 of the labyrinth seal 3 can be related to the axial surface 18 of the floating stator 4 of the first part of the shaft seal assembly 25. Particular focus is on the offset of the axial surfaces 17, 18 between the labyrinth seal 3 and the floating stator 4 at the spherical interface 11.

[0031] FIG. 5B shows the seal-shaft integration against a second surface opposite the first surface shown in FIG. 5A during shaft angular and radial misalignment. This figure emphasizes that the axial surface 17 of the labyrinth seal 3 and the axial surface 18 of the floating stator 4 do not align but move (interlock) relative to each other during shaft 1 misalignment. The shaft-seal gap 6 can be maintained in response to shaft 1 misalignment and the overall sealing integrity is not compromised because the sealing integrity of the floating stator 4 against the fixed stator 2 and the sealing integrity of the floating stator 4 against the labyrinth seal 3 can be maintained during shaft 1 misalignment. Those skilled in the art will appreciate that the shaft 1 and shaft seal assembly 25 are circular in shape and therefore the surfaces naturally represent 360 degrees around the shaft 1. 5A and 5B also show a first gap or gap 20 between the floating stator 4 and the fixed stator 20 during relative movement (other than rotation) between the shaft 1 and the housing 30, and a second gap or gap 21 between the floating stator 4 and the fixed stator 2 opposite the first gap or gap 20.

[0032] In Figures 4, 5, 5A and 5B, as the shaft 1 rotates, it undergoes radial, angular or axial movement and the width of the gaps or clearances 20, 21 are shown to change in response to the movement as compared to the gaps or clearances 20, 21 shown in Figures 3, 3A and 3B. The change in size of the clearances 20, 21 indicates that the floating stator 4 may move in response to the movement or angular misalignment of the shaft 1. The shaft seal assembly 25 maintains the shaft seal gap 6 while allowing interlocking between the shaft faces 17, 18, maintaining the spherical interface 11, and radial movement in the first and second clearances 20 and 21, respectively.

[0033] FIG. 6 is a cross-sectional view of a second embodiment of the shaft seal assembly 25 shown in FIG. 2 overpressurized with an alternative labyrinth seal pattern groove 14. In this embodiment, the labyrinth seal pattern groove 14 can be constructed of a friction reducing material such as polytetrafluoroethylene (PTFE), which can be configured to form a clearance close to the shaft 1. PTFE is sometimes called Teflon manufactured and sold by DuPont. PTFE is a plastic that has high chemical resistance, low and high temperature performance, weather resistance, low friction, electrical insulation, thermal insulation, and high lubricity. Carbon or any other material, including but not limited to, can be substituted for PTFE to provide the necessary sealing and lubrication qualities to the labyrinth seal pattern groove 14.

[0034] As shown in FIG. 6, pressurized sealing fluid can be provided to overpressurize the lubricating labyrinth pattern 26. The pressurized sealing fluid can be introduced into the annular groove 23 of the throttle 26 through one or more inlets. The throttle 26 is sometimes referred to by those skilled in the art as an "alignment skate." The throttle 26 can allow the labyrinth seal 3 to accommodate the movement of the shaft 1 caused by misalignment of the shaft 1. The pressurized sealing fluid can pass through a close clearance formed between the shaft 1 and the labyrinth seal 3 with the throttle 26. The close proximity of the throttle 26 to the shaft 1 can also provide resistance to the flow of sealing fluid over the shaft 1 and allow pressure to build up inside the annular groove 23. The cooperation and connection of the floating annular groove 27 with the annular groove 23 can also provide an outlet for excess sealing fluid to flow away from the shaft seal assembly 25 to equalize pressure or maintain a continuous fluid discharge on the shaft seal assembly 25 during operation. An advantage provided by this embodiment of the shaft seal assembly 25 is in applications where "clean-in-place" product-seal decontamination procedures are preferred or required. Examples include food grade applications.

[0035] FIG. 7 shows the shaft seal assembly 25 with the anti-rotation pin 12 removed to better view the inlets. These inlets typically, but not exclusively, consist of a series of ports, inlets or passages around the circumference of the shaft seal assembly 25. FIG. 7 also shows that the shape and pattern of the labyrinth seal 3 can vary from one embodiment of the shaft seal assembly 25 to the next. The shape of the throttle 26 can also vary as shown by the square outline presented by the throttle groove 22 in addition to the circular type 26. It should also be noted that when direct contact with the shaft 1 is not desired, the shaft seal assembly 25 can be used in combination with a separate sleeve 24 that is attached to the shaft 1 by variable means.

[0036] 8 illustrates another embodiment of the shaft seal assembly 25 in which the shaft seal assembly 25 is secured to the vessel wall 34. The shaft seal assembly 25 may be secured to the vessel wall 34 through fastening members (such as, but not limited to, assembly bolts 33) to ensure improved sealing when the shaft 1 experiences angular misalignment. The assembly bolts 33 and slots (not numbered) passing through the exterior of the shaft seal assembly 25 are one structure and method of assembling the shaft seal assembly 25 to the housing 30. However, any suitable structure and / or method may be used without limitation.

[0037] In certain applications, particularly those where pressure is increased on the work side of the shaft seal assembly 25 (generally the area to the left of the shaft seal assembly 25 as shown in Figures 3-3B and 5-7), it is desirable for the shaft seal assembly 25 to be configured to balance the pressures experienced by the shaft seal assembly 25 in the axial direction. A pressure balancing shaft seal assembly 40 that balances pressures (in the axial direction) is shown in Figures 9-12 where the product is applied against the labyrinth seal inner surface 42 and the floating stator inner surface 44.

[0038] In a first embodiment of the pressure balanced shaft seal assembly shown in Figures 9-10B, the shaft seal member (i.e., labyrinth seal 3 in combination with floating stator 4) includes a pressure balanced annular passage 46. Other than the pressure balanced passage 46, the pressure balanced shaft seal assembly 40 can be operated generally similarly to the shaft seal assembly 25 shown in Figures 1-8 detailed above. That is, the floating stator 4 can be disposed in a fixed stator annular groove 48. The first floating stator / fixed stator gap 20 (shown in Figures 9A and 9B), which in the illustrated embodiment may be between the floating stator radial outer surface 45 and the annular groove radial inner surface 48a, can at least account for radial disturbances of the shaft 1 relative to the housing 30. The spherical interface 11 between the floating stator 4 and the labyrinth seal 3 can at least account for angular disturbances of the shaft 1 relative to the housing 30.

[0039] The pressure balancing annular passage 46 may be formed in the floating stator 4 adjacent to a first radial interface 47a between the floating stator 4 and the fixed stator 2, as shown in Figures 9-10 of the first embodiment. As shown in various embodiments illustrated herein, the first radial interface 47a between the floating stator 4 and the fixed stator 2 may be adjacent to a portion of the fixed stator 2 created by the cavity of the anti-rotation device 16. That is, the axial surface of the floating stator 4 is disposed within the fixed stator 2 and is furthest from the working side of the pressure balancing shaft seal assembly 40. A second radial interface 47b between the floating stator 4 and the fixed stator 2, which may be substantially parallel to the first radial interface 47a, may be disposed closer to the working side of the pressure balancing shaft seal assembly 40 compared to the first radial interface 47a.

[0040] In many applications, the optimum radial dimension of the pressure balancing annular passage 46 may be substantially similar to the radial dimension of the floating stator inner surface 44, and the area of ​​the floating stator 4 on which the product acts and the area of ​​the floating stator 4 on which the sealing fluid acts may have relatively equal surface areas. In such a configuration, when the product and the sealing fluid are pressurized to approximately the same value, the axial forces may be generally balanced. Thus, the optimum radial dimension of the pressure balancing annular passage 46 may be determined according to the design characteristics of the overall system, and the radial dimension of the pressure balancing annular passage 46 may be any suitable amount for a particular application, whether it is greater or less than the radial dimension of the floating stator inner surface 44. The axial dimension of the pressure balancing annular passage 46 may also vary according to the design characteristics of the overall system, including but not limited to the particular sealing fluid used, the pressure of the product, and the pressure of the sealing fluid. In some applications, the optimum dimension of the pressure balancing annular passage 46 is 0.005 inches, but in other embodiments it may be greater and in other embodiments it may be less.

[0041] The pressure balancing annular passage 46 may allow sealing fluid to be introduced into the first gap between the floating stator and the fixed stator 20 (where the sealing fluid may enter the pressure balancing annular passage 46) and act on the floating stator 4 in the axial direction. Typically, the working side of the pressure balancing shaft seal assembly 40 (generally the area to the left of the pressure balancing shaft seal assembly 40 as shown in Figures 9-12) is subjected to forces from the process fluid acting on the labyrinth seal inner surface 42 and the floating stator inner surface 44. These forces are often due in large part to pressures generated by rotating equipment coupled to the shaft 1. For example, coupling the shaft 1 to a fluid pump that generates a head pressure of 70 pounds per square inch (psi) may pressurize the working side of the pressure balancing shaft seal assembly 40 to approximately 70 psi. The pressurized fluid acts on the labyrinth seal inner surface 42 and the floating stator inner surface 44, and thus may urge the labyrinth seal 3 and the floating stator 4 axially away from the working side of the pressure balanced shaft seal assembly 40 (i.e., generally to the right in the drawings shown in FIGS. 9-12). In contrast, depending on the design of the sealing fluid system, the sealing fluid located within the pressure balancing annular passage 46 may urge the labyrinth seal 3 and the floating stator 4 axially toward the working side of the pressure balanced shaft seal assembly 40, substantially countering the axial force that the product exerts on the pressure balanced shaft seal assembly 40.

[0042] Figures 11 and 12 show second and third embodiments, respectively, of a pressure balanced shaft seal assembly 40. The second and third embodiments of the pressure balanced shaft seal assembly 40 generally correspond to the second and third embodiments of the shaft seal assembly 25 shown in Figures 7 and 8 and described in detail above. However, as with the first embodiment of the pressure balanced shaft seal assembly 40 shown in Figures 9-10B, the second and third embodiments include a pressure balanced annular passage 46.

[0043] Various embodiments of the pressure balanced shaft seal assembly 40 shown and described herein can be formed with a fixed stator 2 and a floating stator 4 that can be made of two different parts. These embodiments can facilitate assembly of the pressure balanced shaft seal assembly 40 because, in the embodiments shown herein, a majority of the floating stator 4 can be located within the fixed stator 2. When the pressure balanced shaft seal assembly 40 according to the first embodiment (shown in Figures 9-10B) is installed, a first portion of the fixed stator 2 (i.e., a portion adjacent to the working side of the pressure balanced shaft seal assembly 40) can be fixed to the housing 30. The floating stator 4 and labyrinth seal 3 can then be placed as a single assembly between the shaft 1 and the first portion of the fixed stator 2 (the components that form the spherical interface 11 have been preassembled). When the floating stator 4 and labyrinth seal 3 are placed within the fixed stator 3, a second axial interface 47b can be formed between the fixed stator 2 and the floating stator 4. Finally, the second portion of the fixed stator 2 (i.e., the portion furthest from the working side of the pressure balancing shaft seal assembly 40) can be positioned adjacent to and secured to the first portion of the fixed stator 2. The positioning of the second portion of the fixed stator 2 can then form a first radial interface 47a between the fixed stator 2 and the floating stator 4.

[0044] Alternatively, the floating stator 4 and the labyrinth seal 3 can be disposed separately in the fixed stator annular groove 48. For example, the first part of the fixed stator 2 can be secured to the housing 30, and then the first part of the floating stator 4 can be disposed in the fixed stator annular groove 48. The disposition of the first part of the floating stator 4 in the fixed stator annular groove 48 can form a second axial interface 47b between the fixed stator 2 and the floating stator 4. The labyrinth seal 3 can then be disposed adjacent to the axis 3, and the disposition of the labyrinth seal 3 can form a portion of the spherical interface 11 between the floating stator 4 and the labyrinth seal 3. The second part of the floating stator 4 can then be disposed adjacent to the first part of the floating stator 4 and secured to the first part by a plurality of anti-rotation pins 8, thereby completing the spherical interface 11 between the floating stator 4 and the labyrinth seal 3. Finally, the second portion of the fixed stator 2 may be secured to the first portion of the fixed stator 2 by, but not limited to, a plurality of bolts, rivets, or other fasteners, and the arrangement of the second portion may define a first axial interface 47a between the floating stator 4 and the fixed stator 2. In any embodiment of the shaft seal assembly 25 or pressure balancing shaft seal assembly 40, without limitation, any suitable fastening member known to one of ordinary skill in the art may be used to secure the first and second portions of the floating stator 4 to one another or the first and second portions of the fixed stator 2 to one another.

[0045] FIG. 13 illustrates another embodiment of a bearing separator 18 (or shaft seal assembly) assembled adjacent to a shaft 10. The shaft 10 may extend through the bearing separator 18 and / or through a housing 19. A gas or fluid source 100, which may include, but is not limited to, water, gas, steam, and / or lubricant, may also be in communication with the bearing separator 18 via a conduit 99. The rotor 20 may be secured to the shaft 10 by a friction seal 60, which may be configured as one or more O-rings. The rotor 20 may be configured to follow the rotational movement of the shaft 10 due to the frictional engagement of the seal 60. The passages 40 and 40a may be configured as shown, but will not be described in detail herein, as such a description is already understood by those skilled in the art.

[0046] A pair of corresponding spherical surfaces 50 and 51 can be used to provide a self-aligning radial gap 52 between the rotor 20 and the stator 30 before, during, and after use. This gap 52 can be maintained at a constant value even if the shaft 10 becomes misaligned during use. Various amounts and directions of misalignment between the centerline of the shaft 10 and the housing 19 are illustrated in Figures 15-17. An annular recess 102 between the stator 30 and the fixed stator 31 can allow the bearing separator 18 to accommodate a predetermined amount of radial shaft displacement.

[0047] In the embodiment shown herein, the spherical surfaces 50, 51 may have a center point that is the same from both the axial planes of the rotor 20 and the stator 30, respectively. However, the spherical surfaces 50, 51 may be radially and / or vertically spaced apart as shown. These spherical surfaces 50, 51 may move radially depending on and / or in relation to and / or in cooperation with the radial placement of other components of the bearing isolator 18. Typically, if the shaft 10 becomes misaligned with respect to the housing 19, the rotor 20 becomes misaligned with respect to the housing 19, and then the spherical surfaces 50, 51 and / or the stator 30 moving radially within the annular recess of the fixed stator 31 may compensate for this misalignment.

[0048] 15 and 15A show that in one embodiment of bearing isolator 18, when shaft 10 becomes misaligned with respect to housing 19, rotor 20 may move relative to stators 30, 31 through interaction between spherical surfaces 50 and 51. Such relative movement helps ensure the distance between the center points of rotor 20 and stator 30 and fixed points on housing 19 remains constant or relatively constant during use.

[0049] In the embodiment of the bearing isolator 18 shown in Figures 14 and 14A, the spherical surfaces 50, 51 may be located on the fixed stator 31 and stator 31a, respectively, rather than on the rotor 20 and stator 30. With further reference to Figures 14 and 14A, this design may allow the rotor 20 and stator 31a to move relative to the fixed stator 31, the flanged unit 61a, and / or the housing 19. The rotor 20, stator 31a, and fixed stator 31 may move radially relative to the flanged unit 61a (and thus relative to the housing 19), as best shown in Figure 14A. In this embodiment of the bearing isolator 18, the relative rotation between the spherical surfaces 50 and 51 may be fairly minimal.

[0050] The embodiment of the bearing separator 18 shown in Figures 14 and 14A can provide controlled radial movement of the fixed stator 31, stator 31a and / or rotor 20 relative to the flanged unit 61a, which can engage the housing 19. Rotational movement of the fixed stator 30 relative to the flanged unit 61a can be prevented by anti-rotation pins 101. The fixed stator 31 can be frictionally secured to the flanged unit 61a using friction seals 61, which can be made of any material that has sufficient elastic and frictional properties to hold the fixed stator 31 in a fixed radial position relative to the flanged unit 61a, but still responds to radial forces when the shaft 10 is in a misaligned state. Changes in the radial position of the fixed stator 31, stator 31a and / or rotor 20 and the resulting positions thereof (as well as the resulting position of the interface between the fixed stator 31 and stator 31a) may occur until the radial force is fully accommodated or the maximum radial displacement of the bearing separator 18 is reached.

[0051] 15 and 15A, in operation, the rotor 20 may move radially if the shaft 10 is misaligned with respect to the housing 19. Radial movement of the spherical surfaces 50, 51 between the stator 31a and the fixed stator 31 may result from this pressure. FIG. 15 illustrates the possible radial movement that may result with respect to the center point 80 when the shaft 10 is in a misaligned state. During normal operation, the shaft 10 is typically horizontal with respect to the orientation shown in FIG. 15, as represented by line A. If the shaft 10 is misaligned as represented by line B, the center point 80 may move to a point along line A''. If the shaft 10 is misaligned as represented by line B', the center point 80 may move to a point along line A'. However, in other shaft 10 misalignments, the radial position of the rotor 20, stator 30 and / or fixed stator 31 may remain constant, and the spherical surfaces 50, 51 may compensate for the misalignment of the shaft 10. From the above discussion, it is apparent that the bearing separator 18 is able to provide a constant seal around the shaft 10 because the distance between the spherical surfaces 50 and 51 can remain constant regardless of any misalignment of the shaft 10, whether that misalignment is normal or due to a design nature.

[0052] The physical dimensions of spherical surfaces 50 and 51 can vary in linear value and distance from center point 80 depending on the particular application of bearing separator 18. These variations can be utilized to accommodate different sized shafts and seals and different amounts of misalignment, and thus are in no way intended to limit the scope of bearing separator 18 disclosed herein. Additionally, any suitable structure and / or method of rotational engagement, fixed engagement, or engagement with various degrees of freedom between the various elements can be used with shaft seal assembly 18, including, without limitation, screws, bolts, pins, chemical adhesives, interference fits, and / or combinations thereof.

[0053] Another embodiment of the shaft seal assembly 10 is shown in Figures 16A and 16B. This embodiment is similar to the embodiment of the shaft seal assembly 25 shown in Figures 1-12 above. The shaft seal assembly 10 can include a fixed stator 20, a floating stator 30, and a sealing member 40, as shown. In the illustrated embodiment, the sealing member 40 can be disposed adjacent to the shaft 12, which is rotatable relative to the shaft seal assembly 10 and / or the housing. Thus, a rotational interface can exist between a radially inner surface 46 of the sealing member 40 disposed adjacent to the shaft 12 and an outer portion of the shaft 12. In other embodiments of the shaft seal assembly 10, not shown here, the sealing member 40 can be engaged with the shaft 12 such that the sealing member 40 rotates with the shaft 12 (e.g., the shaft seal assembly 10 can be configured with a rotor). In such an embodiment, a rotational interface can exist between a concave surface 38 of the floating stator 30 and a convex surface 48 of the sealing member 40. Thus, the scope of the shaft seal assemblies 10 disclosed herein extends to shaft seal assemblies 10 in which the sealing member 40 either rotates with the shaft 12 or does not rotate with the shaft 12 .

[0054] The embodiment of the shaft seal assembly 10 shown in FIGS. 16A and 16B may include a stationary stator 20 that may be securely assembled to a housing (not shown in FIGS. 16A and 16B ) by any suitable method and / or structure. The stationary stator 20 may include a main body 21 and a face plate 22 that may engage with one another via one or more fasteners 14. It is contemplated that the stationary stator 20 formed with the main body 21 and face plate 22 may facilitate installation of the shaft seal assembly 10 in certain applications. In such applications, the main body 21 may be secured to the housing, the sealing member 40 and the floating stator 30 may be appropriately positioned, and then the face plate 22 may be secured to the main body 21. However, the scope of the present disclosure is in no way limited to a particular assembly and / or installation method of the shaft seal assembly 10.

[0055] The fixed stator 20 may be formed with an annular recess 26, and a portion of the floating stator 30 and / or the sealing member 40 may be disposed within the annular recess 26. A predetermined clearance between the radial outer surface 32 of the floating stator 30 (and the axial outer surface of the floating stator 30) and the inner surface of the annular recess 26 may be selected to allow a predetermined amount of relative radial and / or axial movement between the fixed stator 20 and the floating stator 30. At least one pin 34 (which may be radially oriented as in the embodiment shown in Figures 16A and 16B) may engage the floating stator 30 at a second pin recess 35, and a portion of the pin 34 may extend into a recess 42 formed in the sealing member 40. Additionally, another pin (not shown, but which may be axially oriented) may also engage the floating stator about the first pin recess 33, and a portion of this pin may extend into the faceplate pin recess 22a. 16A and 16B, pins 35 can mitigate relative rotation between the floating stator 30 and the sealing member 40. Axially oriented pins (not shown) can mitigate relative rotation between the floating stator 30 and the stationary stator 20. The axial interface between the floating stator 30 and the stationary stator 20 can be sealed by a seal 28, which can be disposed in the stationary stator seal groove 20a and / or the faceplate seal groove 22b. The seal 28 can be configured as an O-ring, but other embodiments of the shaft seal assembly 10 are not limited and may be configured differently.

[0056] The floating stator 30 may also be formed with a concave surface 38 within a radially inner portion thereof which may form a hemispherical interface with a corresponding convex surface 48, which is formed within a radially outer portion of the sealing member 40. Thus, the shaft seal assembly 10 shown in Figures 16A and 16B may accommodate misalignment of the shaft 12, radial movement of the shaft 12, and axial movement of the shaft 12 relative to the shaft seal assembly 10 and / or the equipment housing in the same and / or similar manner as previously described for the shaft seal assembly 25 shown in Figures 1-12.

[0057] Exemplary embodiments of the shaft seal assembly 10 may also include various fluid conduits that add sealing fluid to the shaft seal assembly 10. The stationary stator 20 may be formed with one or more inlets 24 that introduce sealing fluid to the shaft seal assembly 10. The inlets 24 may be in fluid communication with an annular recess 26 formed in the stationary stator 20, which in turn may be in fluid communication with one or more radial passages (not shown) formed in the floating stator 30 and extending from the radially outer surface 32 to the concave surface 38 of the floating stator 30. As an alternative or in addition to the one or more radial passages, the second pin recess 35 formed in the floating stator 30 may be configured to allow sealing of a certain amount of fluid radially inwardly across a length of the second pin recess 35. A radially inner end of the second pin recess 35 may be formed with a second pin recess enlarged portion 35a. Alternatively, the floating stator 30 may be formed with the floating stator annular groove 37 on the concave surface 38 of the floating stator annular groove 37. These radial passages, the second pin recess 35, the second pin recess enlarged portion 35a, and / or the floating stator annular groove 37 may act as conduits to seal fluid from the annular recess 26 of the fixed stator 20 to the convex surface 48 of the sealing member 40. Thus, the scope of the shaft seal assembly 10 is not limited by the particular combination of fluid conduits disclosed herein, but rather extends to all configurations of fluid conduits that may supply sealing fluid to the sealing member 40.

[0058] The fixed stator 20 and / or the seal 28 between the fixed stator 20 and the floating stator 30 may be configured such that a majority of the sealing fluid introduced into the inlet 24 passes radially inwardly through the floating stator 30 (by any of the fluid conduit configurations described above). The hemispherical interface between the concave surface 38 of the floating stator 30 and the convex surface 48 of the sealing member 40 may be sealed by the seal 28, which may be disposed within the floating stator seal groove 30a and / or the sealing member seal groove (not shown). The seal 28 may be configured as an O-ring, although any suitable structure and / or method may be used without limitation. The floating stator 30, the sealing member 40, and / or the seal 28 between the floating stator 30 and the sealing member 40 may be configured so that a majority of the sealing fluid exiting the floating stator 30 passes through the sealing member 40 through a plurality of radial holes 44 in a direction from the convex surface 48 to the radially inner surface 46 of the sealing member 40 (i.e., the sealing fluid may be configured to exit the shaft seal assembly 10 adjacent the shaft 12 in a generally radially inward direction).

[0059] The fixed stator 20, floating stator 30 and / or sealing member 40 may be configured with fluid conduits formed therein to allow a majority of the sealing fluid to exit the shaft seal assembly 10 from the region between the sealing member 40 and the shaft 12 at a predetermined rate for a given set of operating parameters (e.g., sealing fluid viscosity, pressure and / or volumetric flow rate, rpm of the shaft 10, etc.). An exemplary embodiment of the shaft seal assembly 10 may be formed with 32 radial holes 44 in the sealing member 40, with corresponding pairs equally spaced around the circumference of the sealing member, as best shown in FIGS. 17A and 17B. Each radial hole 44 may be formed with a radial hole inlet 44a adjacent the convex surface 48 and a radial hole outlet 44b adjacent the radial inner surface 46. However, in other embodiments of the sealing member 40 not illustrated in this specification, the sealing member 40 may be formed with, without limitation, differently configured radial holes 44, a different number of radial holes 44, and / or different relative positions of the radial holes 44.

[0060] It is contemplated that the configuration of radial holes 44 shown in the embodiment of sealing member 40 shown in Figures 17A and 17B may be more efficient than other configurations in that it may require a lower volumetric flow rate of sealing fluid for a given set of operating parameters when compared to the prior art. Additionally, the smooth, generally cylindrical configuration of radially inner surface 46 may provide a pressurized fluid barrier (e.g., a "lift-off seal") between shaft 12 and sealing member 40 at their interface. This may result in a substantially frictionless shaft seal assembly 10, with no and / or minimal contact between shaft 12 and sealing member 40 during operation. However, in other embodiments, different numbers, spacings and / or configurations of fluid conduits may be used within stationary stator 20, floating stator 30 and / or sealing member 40 without departing from the spirit and scope of the shaft seal assembly 10 disclosed and claimed herein.

[0061] In light of the present disclosure, it will be apparent to one of ordinary skill in the art that the fluid conduit configurations disclosed herein may be adapted to create a pressurized fluid barrier between any interface where two elements rotate relative to one another, such as, for example, the interlocking seals disclosed in U.S. Pat. No. 7,090,403, which is incorporated herein by reference in its entirety, and discloses shaft seal assembly embodiments having a spherical rotating interface between a rotor and a floating stator (such as those shown in FIGS. 13, 15, and 15A), and shaft seal assembly embodiments having a generally non-rotating spherical interface between two portions of a stator (such as those shown in FIGS. 14 and 14A). Thus, the scope of the shaft seal assembly 10 disclosed herein is not limited to the location and / or type of rotating interface configured to accommodate the shaft seal assembly 10.

[0062] For example, in one embodiment not shown, an embodiment of the stator 30 similar to that shown in Figures 13, 15 and 15A can be configured with one or more generally narrow diameter radial holes (the holes can be substantially similar to those shown in the embodiment of Figures 17A and 17B). Such radial holes can be configured to bring fluid from an external source (which can be in fluid communication with the passages 40) to an interface between spherical surfaces on the stator portions 31, 31a (the interface can be configured as a concave surface on the stator 31 and a convex surface on the stator 31a). Alternatively, the stator 31 can be configured with radial holes that serve to bring fluid from an external source (which can be in fluid communication with the passages 40) to an interface between the stator 31a and the rotor 20, which can be a rotating interface having a labyrinth seal pattern and / or one or more seals (which can be configured as O-rings) therein.

[0063] Further embodiments of the shaft seal assembly 18-21B, other features and components of various exemplary embodiments of a generally ring-shaped seal assembly 100 having a central bore are now shown. Generally, the exemplary embodiments of the seal assembly 100 may provide all or a portion of the various advantages of the shaft seal assembly 10 and bearing separator 18 disclosed herein in addition to one or more advantages inherent to the shaft seal assembly 100 shown in Figures 18-21B, unless otherwise specified in the claims below, without limitation. Generally, the seal assembly 100 can accommodate misalignment of the shaft 12 relative to a housing (not shown) and / or seal assembly 100 via a hemispherical interface between the first stator 110 and the second stator 120, accommodate movement of the shaft 12 in the radial dimension relative to the housing and / or first stator 110 and second stator 120 via movement of the throttle member 130 relative to the first stator 110 and second stator 120 in the radial dimension, and / or accommodate movement of the shaft 12 relative to the housing and / or seal assembly 100 in the axial dimension via circumferential gaps and voids between the inner surface of the throttle member 130 and the outer surface of the shaft 12, unless otherwise specified in the claims below, without limitation.

[0064] The seal assembly 100 shown in Figures 18-21B may be engaged with an equipment housing (not shown) such that the shaft 12 extends from and is rotatable relative to the equipment housing. The seal assembly 100 may be engaged with the equipment housing via one or more mechanical fasteners 14, but any suitable method and / or device (e.g., without limitation, welding, chemical adhesives, interference fit, etc.) may be used to satisfactorily engage the seal assembly 100 with the equipment housing unless otherwise provided in the claims below.

[0065] The seal assembly 100 may include a first fixed stator 110, a second stator 120, and a throttle member 130. With specific reference to Figures 18A-18C, which provide cross-sectional views of the seal assembly 100 along various lines shown in Figure 18, it is contemplated that the seal assembly 100 may be configured such that the inner side (or product side) of the seal assembly 100 is generally to the right of Figures 18A and 18C and generally to the left of Figure 18B, and the outer side of the seal assembly 100 is generally to the left of Figures 18A and 18C and generally to the right of Figure 18B, unless otherwise specified in the claims below, without limitation. The axial face of the seal assembly 100 shown in Figures 19 and 19A is generally inner, while the right side of Figure 19B is generally inner and the left side of Figure 19B is generally outer, unless otherwise specified in the claims below, without limitation. The exploded perspective views of the seal assembly 100 shown in Figures 19C and 19D are shown from opposite sides of the seal assembly 100, with Figure 19C showing generally from the inside while Figure 19D showing generally from the outside, unless otherwise specified in the claims below, but without limitation.

[0066] The first stator 110 may be formed with an inlet 114a that may provide a sealing fluid. The terminus of the inlet 114a adjacent the second stator 120 may be formed as or disposed adjacent a ledge 112a in the concave surface 112 of the first stator 110, as described in further detail below. Additionally, the first stator 110 may be formed with an annular recess 111 on an inner surface of the first stator 110, and an O-ring 102 may be disposed within the annular recess 111. It is contemplated that the O-ring 102 may sufficiently seal the interior of the first stator 110 against the equipment housing to reduce or prevent ingress of material toward a product adjacent the equipment housing and escape of the product at the interface between the seal assembly 110 and the equipment housing. However, without limitation, any suitable structure and / or method may be used to achieve the desired seal between the seal assembly 100 and the equipment housing (e.g., other mechanical sealing devices, chemical seals, combinations thereof, etc.), unless otherwise specified in the claims below.

[0067] It is contemplated that in many applications it may be advantageous to pressurize the sealing fluid in the manner already described above for the other shaft seal assemblies 10 and / or bearing separators 18. The sealing fluid may include, but is not limited to, liquid, vapor, gas, and / or combinations thereof, unless otherwise specified in the following claims. The optimal sealing fluid and sealing fluid pressure will vary from one application of the seal assembly 100 to the next and will depend at least on the compatibility of the sealing fluid with other system components, including but not limited to products adjacent to the equipment housing with which the seal assembly 100 engages. It is contemplated that air, nitrogen, water, and / or steam may be suitable sealing fluids for certain applications. Thus, the phase, chemical composition, properties, configuration, etc. of the sealing fluid in no way limit the scope of the present disclosure, unless otherwise specified in the following claims.

[0068] The first stator 110 can be formed with one or more pin recesses 116a into which the pins 108 can be inserted. The radially inner ends of the pins 108 can extend into the pin recesses 123 of the second stator, as described in more detail below, and can serve to limit the amount of angular misalignment between the first stator 110 and the second stator 120.

[0069] The first stator 110 may be configured with a concave surface 112 on a portion thereof. The first stator 110 may be configured with one or more annular recesses 111 on the concave surface 112, and an O-ring 102 may be disposed within each annular recess 111 to suitably mitigate or prevent escape and / or ingress of material through a region between the first stator 110 and the second stator 120 at an interface between the concave surface 112 of the first stator 110 and the convex surface 122a of the second stator 120 (the second stator is described in more detail below).

[0070] The second stator 120 may be formed with a main body 122 and an access plate 128 that may be selectively engaged with one another via one or more fasteners 104, which may pass through a portion of the access plate 128 via one or more axial holes 128b formed therein. However, without limitation, any suitable method and / or device (e.g., welding, chemical adhesives, etc.) may be used to sufficiently engage the main body 122 with the access plate 128, unless otherwise specified in the claims below. The main body 122 may be formed with one or more second stator inlets 124, which may be in fluid communication with the inlets 114a formed in the first stator 110. Generally, the second stator inlets 124 may act as a passageway to seal fluid traveling from the first stator 110 to the radially inner surface of the second stator 120 (and then through a throttle member 130, which will be described in more detail below). The main body 122 can be formed with a convex surface 122a on its exterior, which can correspond to the concave surface 112 on the radially inner portion of the first stator 110, creating a hemispherical interface between the first stator 110 and the second stator 120. It is contemplated that for certain applications, it may be beneficial to configure the second stator 120 with a plurality of second stator inlets 124 disposed around an outer periphery of the second stator 120 (at least as shown in FIG. 19C ), although the scope of the present disclosure is not so limited unless otherwise provided in the claims below.

[0071] As shown in FIGS. 18A-18C, the convex surface 122a can be entirely confined to the main body 122, such that the surface of the access plate 128 does not constitute any part of the convex surface 122a. However, in other embodiments, the portion of the convex surface 122a can extend into the access plate 128, unless otherwise specified in the claims below, without limitation. The convex surface 122a can be formed with a convex shelf 122b, which can be disposed adjacent to a shelf 112a formed in the concave surface 112 of the first stator 110. The convex shelf 122b can be configured to be approximately linear in the axial dimension. The convex shelf 122b can act in conjunction with the shelf 112a in the first stator 110 to provide a specific amount of sealing fluid in the interface between the first stator 110 and the second stator 120. Thus, without limitation, unless otherwise specified in the claims below, the optimal configuration (e.g., size, shape, etc.) of the ledge 112a and / or the convex ledge 122b may vary from one application of the seal assembly 100 to the next.

[0072] A portion of the convex surface 122a and / or the convex shelf 122b can be formed with a second stator pin recess 123 that can receive a distal end of the pin 108, as briefly described above and illustrated in at least FIG. 21B. The second stator pin recess 123 and the pin 108 can be configured to limit the amount of angular misalignment between the first stator 110 and the second stator 120 during operation due to the interaction between the second stator pin recess 123 and the pin 108. The interaction between the pin 108 and the second stator pin recess 123 can also serve to ensure an appropriate amount of axial misalignment and / or relative rotation between the first stator 110 and the second stator 120. In one embodiment of the seal assembly 100, two pins 108 may be employed, with a first pin 108 associated with one second stator pin recess 123 disposed at the 12 o'clock position and a second pin 108 associated with the other second stator pin recess 123 disposed at the 6 o'clock position, as shown at least in FIG. 21B. However, without limitation, any number and / or configuration of pins 108 and associated second stator pin recesses 123 may be used with the seal assembly 100, unless otherwise provided in the claims below. For example, in other embodiments, the pins 108 may be configured to be disposed at different axes of rotation.

[0073] The main body 122 and the access plate 128 may be configured such that the access plate 128 is accessible when the shaft seal assembly 100 is engaged with the equipment housing. Additionally, the second stator 120 may be configured such that the access plate 128 may be selectively removed from the main body 122 to allow a user to access the throttle member 130 and / or other internal components of the seal assembly 100 without removing the entire seal assembly 100 from the equipment housing. Such a configuration is contemplated to allow a user to replace the throttle member 130 and / or other internal components of the seal assembly 100 relatively easily as compared to the prior art (e.g., without requiring removal and / or separation of the seal assembly 100 from the equipment housing).

[0074] The main body 122 may be formed with a main body shelf 126, a radially inner surface of which may be generally linear in the axial dimension, and the main body shelf 126 may extend axially toward the exterior of the shaft seal assembly. A radially outer portion of the access plate 128 may engage the main body 122 at the main body shelf 126, and the outer axial limit of the main body 122 is equal to or approximately equal to the outer axial limit of the access plate 128. However, in other embodiments, the outer axial limit of the main body 122 may be greater than the outer axial limit of the access plate 128, and in other embodiments, the outer axial limit of the access plate 128 may be greater than the outer axial limit of the main body 122. Thus, the scope of the present disclosure extends, without limitation, to all of these various configurations and others, unless otherwise set forth in the following claims. The access plate 128 may be formed with a shoulder 128a which may extend axially inwardly towards the main body 122 and which may have one or more axial holes 128b formed as already described above.

[0075] The main body 122 and the access plate 128 may cooperate to define an internal passage 125 on a radially inner surface of the second stator 120. An axial wall on the inside of the main body 122 may provide a first axial restriction to the internal passage 125, and an inner axial surface of the access plate 128 may provide a second axial restriction to the internal passage 125. The internal passage 125 may be configured such that a radial dimension of the internal passage 125 varies axially, as shown at least in FIG. 18A, with the radial dimension of the internal passage 125 adjacent the intermediate portion 133 and the second wall 134 of the throttle member 130 being greater than the radial dimension adjacent the first wall 132 of the throttle member 130. However, without limitation, other configurations of radial dimensions of the internal passage 125 may be used with the seal assembly 100, unless otherwise specified in the claims below.

[0076] Either the first wall 132 or the second wall 134 of the throttle member 130 may be formed with a throttle member annular recess 131 within which an O-ring may be disposed, as shown in at least the exemplary embodiment of Figures 18A-19D. Alternatively or additionally, an axial wall of the main body 122 or the inner axial surface of the access plate 128 may include a second stator annular recess 121 within which an O-ring 102 may be disposed, as shown in the exemplary embodiment of Figures 21A and 21B. It is contemplated that the O-ring 102 disposed within the second stator annular recess 121 formed in the main body 122 and / or the O-ring disposed within the throttle member annular recess 131 formed in the second wall 134 may be sufficient to seal the interface between the main body 122 and the throttle member 130. It is further contemplated that the O-ring 102 disposed within the second stator annular recess 121 formed in the access plate 128, and / or the O-ring 102 disposed within the throttle member annular recess 131 formed in the first wall 132, may sufficiently seal the interface between the access plate 128 and the throttle member 130 to reduce or prevent the ingress of material and / or the escape of sealing fluid at such interface. However, without limitation, any suitable structure and / or method may be used to achieve the desired seal between the main body 122 and the throttle member 130 and / or between the access plate 128 and the throttle member 130 (e.g., other mechanical sealing devices, chemical seals, combinations thereof, etc.), unless otherwise specified in the claims below.

[0077] As shown at least in Figures 18A-18C, 19A, and 21B, the internal passage 125 can have a variety of outer diameters and / or surfaces on the internal passage 125. For example, a portion of the internal passage 125 formed in the main body 122 can be configured with a transition surface from an axial surface to a radial surface that is smooth and / or rounded. In contrast, another portion of the internal passage 125 formed in the access plate 128 can be configured with a transition surface from an axial surface to a radial surface that is perpendicular. The optimal configuration of the internal passage 125 (e.g., actual volume, relative volume, shape, axial dimensions, radial dimensions, etc.) can vary from one application of the seal assembly 100 to the next, and thus is in no way intended to limit the scope of the present disclosure, unless otherwise provided in the claims that follow.

[0078] The throttle member 130 may be disposed within a portion of the internal cavity 125 in the second stator 120. Generally, the throttle member 130 may be configured with an inner axial surface and an outer axial surface, the inner axial surface may engage with and / or be disposed adjacent to a portion of the main body 122 of the second stator 120, and the outer axial surface may engage with and / or be disposed adjacent to a portion of the access plate 128. A radially inner surface of the throttle member 130 may be disposed adjacent the shaft 12. The throttle member 130 may be configured with a first wall 132 adjacent to the access plate 128, a second wall 134 adjacent to the main body 122 of the second stator 120, and an intermediate portion 133 that may be disposed between the first wall 132 and the second wall 134. Both the first wall 132 and the second wall 134 may extend radially outward such that a throttle member passage 136 exists between the first wall 132 and the second wall 134 .

[0079] The first wall 132 may be formed with one or more first wall axial projections 132a extending therefrom, as shown at least in FIG. 18B, which may correspond to one or more axial recesses 127 formed in the access plate 128. Additionally or alternatively, the second wall 134 may be formed with one or more axial projections 134a extending therefrom, which may correspond to one or more axial recesses 127 formed in the main body 122 of the second stator 120. The axial projections 132a, 134a may be integrally formed with a portion of the throttle member 130 or may be formed separately and subsequently engaged with a portion of the throttle member 130, unless otherwise specified in the claims below, without limitation (the axial projections 132a, 134a may act as a type of pin or dowel). A portion of the axial protrusions 132a, 134a may extend into an axial recess 127 formed in the main body 122 of the second stator 120 and / or an axial recess 127 formed in the access plate 128, without limitation, unless otherwise specified in the claims below, to prevent and / or reduce relative rotational movement between the throttle member 130 and the second stator 120 and / or to limit the amount of relative radial movement therebetween. Alternatively or additionally, the amount of relative radial movement between the throttle member 130 and the second stator 120 may be limited by the configuration of the first wall 132, the second wall 134, the radial inner surface of the main body 122 and / or the radial inner surface of the access plate 128. Specifically, the radial dimensions of these components can be adjusted so that a certain amount of radial movement of the throttle member 130 can occur prior to the end of either the first wall 132 or the second wall 134 contacting a portion of the second stator 120 within the internal passage 125.18A , the configuration of the ends of first wall 132 and the radially inner surface of second stator 120 and / or cap 128 are such that they define an annular space 129 within which throttling member 130 can move in a radial dimension relative to second stator 120 (and thus relative to other components of seal assembly 100). However, the scope of the present disclosure is not so limited unless otherwise defined in the claims below.

[0080] The throttle member passage 136 may be configured to intersect all or a portion of the internal passage 125, and the throttle member passage 136 and the internal passage 125 may cooperate to form an annular cavity within the seal assembly 100. It is contemplated that in certain applications, the throttle member 130 may be configured to preferentially direct sealing fluid within the internal cavity 125 toward a radial passage 133 a formed within the throttle member, and / or toward one or more radial interfaces between the throttle member 130 and the main body 122 and / or between the throttle member 130 and the access plate 128, although the scope of the present disclosure is not so limited unless otherwise set forth in the claims below.

[0081] The intermediate portion 133 of the throttle member 130 may be formed with one or more radial passages 133a that may supply sealing fluid from the internal passage 125 of the second stator 120 through the throttle member 130 to an area radially inward relative to the throttle member 130 (e.g., shaft 12). It is contemplated that the radial passages 133a in the throttle member 130 may be configured in pairs arranged annularly about the throttle member 130. However, the optimal number and configuration (e.g., size, location, etc.) of the radial passages 133a may vary from one application of the seal assembly 100 to the next, and thus in no way limit the scope of the present disclosure unless otherwise provided in the claims that follow. Additionally or alternatively, the first wall 132 and / or the second wall 134 may be configured with axial passages to direct sealing fluid from the internal passages 125 of the second stator 120 through the axial passages in the throttle member 130 to the interface between the throttle member 130 and the main body 122 and / or the interface between the throttle member 130 and the access plate 128. It is contemplated that such a configuration may serve to axially balance pressure across the throttle member 130 and / or the seal assembly 100 in a particular application, without limitation, unless otherwise specified in the claims below.

[0082] As discussed above with respect to the internal passage 125 of the second stator 120, the optimal configuration (e.g., actual volume, relative volume, shape, axial dimension, radial dimension, etc.) of the throttle member 130 and its components (e.g., first wall 132 and its configuration, radial passage 133a and its configuration, intermediate portion 133 and its configuration, second wall 134 and its configuration, throttle member passage 136, axial passages formed in either of the walls 132, 134, etc.) may vary from one application of the seal assembly 100 to the next, and thus is in no way intended to limit the scope of the present disclosure, unless otherwise specified in the claims that follow.

[0083] In general, the seal assembly 100 may be configured such that relative radial movement between the shaft 12 disposed within the central bore of the seal assembly 100 and the seal assembly 100 and / or equipment housing with which the seal assembly 100 engages may be accommodated via relative radial movement between the throttle member 130 and the second stator 120 within the internal passage 125 of the second stator 120. Additionally, the seal assembly 100 may be configured such that relative axial movement between the shaft 12 disposed within the central bore of the seal assembly 100 and the seal assembly 100 and / or equipment housing with which the seal assembly 100 engages may be accommodated via an interface between a radially inner surface of the throttle member 130 and a radially outer surface of the shaft 12. It is contemplated that in many applications, sealing fluid may be provided to this interface via one or more radial passages 133a formed in the throttle member 130, as previously described. The optimal interface clearance between the throttle member 130 and the shaft 12 may vary from one application of the seal assembly 100 to the next, and thus is in no way intended to limit the scope of the present disclosure, unless otherwise specified in the claims that follow. However, it is contemplated that in at least some applications, the clearance may be between 0.001 inches and 0.5 inches, and that the clearance may affect the flow characteristics of the sealing fluid (e.g., a larger clearance may result in a relatively higher volumetric flow rate of sealing fluid under otherwise equal conditions and configurations).

[0084] Generally, but not limited to, unless otherwise specified in the claims below, in various exemplary embodiments of the seal assembly 100, the throttle member 130 may be constructed from any suitable material, including, but not limited to, a polymer (e.g., polyetheretherketone, graphalloy®, nyloil®, carbon, etc.) and / or any other lubricating material.

[0085] 20A and 20B in detail, another exemplary embodiment of a seal assembly 100 according to the present disclosure is shown. In general, this exemplary embodiment may be configured with the same, similar or correlated elements as previously described and shown in FIGS. 18-19D and may provide the same, similar or correlated benefits. However, the seal assembly 100 shown in FIGS. 20A and 20B may be configured such that the first stator 110 may diverge along a horizontally oriented plane, which passes through the longitudinal axis of the shaft 12 about which the seal assembly 100 is disposed. The two portions of the first stator 110 may be referred to as an upper portion 110a and a lower portion 110b. While seal assembly 100 may be installed in an application in which the longitudinal axis of shaft 12 is oriented vertically or at some angle between horizontal and vertical, the terms "upper" and "lower" and the description of a horizontally oriented plane are not intended to limit the scope of seal assembly 100, but rather to affect the relative positions of upper portion 110a and lower portion 110b, unless otherwise specified in the claims below.

[0086] The upper portion 110a and the lower portion 110b can be selectively engaged with one another via one or more fasteners 104, corresponding receivers 105, and corresponding apertures 106. Additionally, alignment pins and / or dowels can be utilized to ensure proper alignment between the upper portion 110a and the lower portion 110b. In an exemplary embodiment, the fasteners 104 can be configured as mechanical fasteners (e.g., bolts, screws, etc.), with each fastener 104 passing through a first aperture 106 formed in the upper portion 110a and a distal end thereof engaging a receiver 105 formed in the lower portion 105, which can be threadedly engaged with corresponding threads formed on the fastener 104. However, any suitable structure and / or method of selectively engaging the upper portion 110a with the lower portion 110b (e.g., other types of mechanical fasteners, clamps, adhesives, etc.) can be used, unless otherwise specified in the following claims, without limitation.

[0087] In certain applications, it may be beneficial to use a first stator 110 comprised of an upper portion 110a and a lower portion 110b. Such a configuration may provide additional axial space outside of the first stator 110, allowing the size of the inlet 114a to be increased as compared to a similarly sized axial seal assembly 110 having an inner member 114 and an outer member 116. Such a configuration may allow for relatively easy replacement of one or more O-rings 102 with a code inventory and / or may not require disassembly of the equipment that the seal assembly 100 engages. In other applications, a first stator 110 comprised of an upper portion 110a and a lower portion 110b may allow for easier installation than a seal assembly 100 having an inner member 114 and an outer member 116 due to a reduced number of fasteners 104. Finally, a first stator 110 comprised of an upper portion 110a and a lower portion 110b may provide manufacturing benefits. This is because fewer elements are required to configure the concave surface 112 as compared to a similarly sized shaft seal assembly 110 having an inner member 114 and an outer member 116. Either the upper portion 110a and / or the lower portion 110b may be configured with one or more slots 113 to assist a user in separating the upper portion 110a from the lower portion 110b and / or in releasing the seal assembly 100 from an associated shaft 12 and / or other equipment.

[0088] In addition to the first stator 110 bifurcating along a horizontally oriented plane passing through the longitudinal axis of the shaft 12 about which the seal assembly 100 is disposed, the second stator 120, the throttle member 130, and / or the access plate 128 may also be so bifurcated. It is contemplated that such a configuration may reduce the labor and / or time associated with installing the seal assembly 100 by allowing installation of the seal assembly 100 about the shaft 12 without the need to disassemble much of the equipment or any of the equipment associated with the shaft 12. In such a configuration, the two halves of any split components (e.g., the first stator 110, the second stator 120, the throttle member 130, the access plate 128, etc.) may be selectively engaged with one another via any suitable structure and / or method as described above with respect to the first stator 110, the upper portion 110a, and the lower portion 110b, unless otherwise provided in the claims below, without limitation.

[0089] 21A and 21B, another exemplary embodiment of a seal assembly 100 according to the present disclosure is shown. Generally, this exemplary embodiment may be configured with the same, similar, or correlating elements as previously described and shown in FIGS. 18-19D and may provide the same, similar, or correlating benefits. However, the seal assembly 100 shown in FIGS. 21A and 21B may be configured such that the first stator 110 may include an inner member 114 and an outer member 116, which may be engaged with one another.

[0090] The inner member 114 of the first stator 110 can be formed with an inlet 114a that can provide a sealing fluid. Additionally, the inner member 114 can be formed with an annular recess 111 on an inner surface of the first stator 110, and an O-ring 102 can be disposed within the annular recess 111. It is contemplated that the O-ring 102 can sufficiently seal the inside of the first stator 110 against the equipment housing to reduce or prevent ingress of material toward a product adjacent the equipment housing and escape of the product at the interface between the seal assembly 110 and the equipment housing. However, without limitation, any suitable structure and / or method can be used to achieve a desired seal between the seal assembly 100 and the equipment housing (e.g., other mechanical sealing devices, chemical seals, combinations thereof, etc.) unless otherwise specified in the following claims.

[0091] The outer member 116 may be formed with one or more pin recesses 116a into which the pins 108 may be inserted. The radially inner ends of the pins 108 may extend into the second stator pin recesses 123, as described in more detail below, and may act to limit the amount of angular misalignment between the first stator 110 and the second stator 120.

[0092] The inner member 114 and the outer member 116 can cooperate to provide a concave surface 112 on their portions, and a first portion of the concave surface 112 can be configured on the inner member 114 and a second portion of the concave surface 112 can be configured on the outer member 116. A shelf 112a can be disposed between the first and second portions of the concave surface 112, and the shelf 112a can be approximately linear in the axial dimension, at least as shown in Figures 18B and 18C. Finally, both the inner member 114 and the outer member 116 can be configured with annular recesses 111 on the concave surface 112, and an O-ring 102 can be disposed within each annular recess 111 to sufficiently reduce or prevent escape and / or ingress of material through the area between the first stator 110 and the second stator 120 at the interface between the concave surface 112 of the first stator 110 and the convex surface 122a of the second stator 120 (the second stator is described in further detail below).

[0093] The seal assembly 100 shown in Figures 18-21B may enjoy several advantages over the prior art. One advantage is that the mass of the elements of the seal assembly 100 that physically move to accommodate movement of the radial axis 12 is less than the mass of such elements of the prior art because only the throttle member 130 is required for physical movement, allowing for a faster response and providing better sealing and a longer life for the seal assembly 100. Another advantage is that the relative axial position of the access plate 128 to the main body 122 may be adjusted by configuring the outer diameter of the access plate 128 with threads that correspond to the threads on the inner diameter of the second stator 120 (which may be formed on the radially inner surface of the main body shelf 126), allowing a user to adjust the amount of compression of the O-ring or O-rings 102 adjacent to the throttle member 130. This may allow a user to adjust the amount of force required to move the throttle member 130 in the radial dimension relative to the second stator 120. The fasteners 104 disposed within the axial holes 128b of the access plate 128 may provide a form of gripping point to rotate the access plate 128 relative to the second stator 120 and / or may provide a locking mechanism (e.g., as a type of set screw) to fix the position of the access plate 128 relative to the second stator 120 (which may otherwise change due to external forces, vibration, etc.).

[0094] The particular configuration, number and / or physical dimensions of the various features of the fixed stator 20, the floating stator 30 and / or the sealing member 40 (e.g., radial dimension of the annular recess 26, surface area of ​​the concave surface 38 and / or the convex surface 48, diameter, length and orientation of the radial hole 44, etc.) may vary depending on the particular application of the shaft seal assembly 10. Additionally, the optimal configuration, number and / or physical dimensions of the various features of the first stator 110 and / or components thereof (e.g., inner member 114, outer member 116, etc.), the second stator 120 and / or components thereof (e.g., main body 122, convex shelf 122b, interior passage 125, access plate 128, etc.), and / or the throttle member 130 and / or components thereof (e.g., first wall 132, intermediate portion 133, second wall 134, throttle member passage 136, etc.) may vary depending on the particular application of the seal assembly 100. These variations can be utilized to accommodate various sizes of shafts 12 and / or shaft seal assemblies 100 as well as various amounts and / or types of relative movement between the shaft 12 and seal assembly 100.

[0095] The materials used to construct the devices and / or device components disclosed herein will vary depending on the particular application, but it is contemplated that polymers, synthetic materials, metals, metal alloys (e.g., bronze, brass, stainless steel or other metals and / or metal alloys and / or combinations thereof), and / or combinations thereof may be particularly useful in some applications. Thus, the above-referenced elements may be constructed from any materials known to those of skill in the art or later developed that are suitable for a particular application of the present disclosure without departing from the spirit and scope of the present disclosure, unless otherwise indicated in the claims that follow.

[0096] Having described the preferred aspects of the various apparatus and methods, as well as other features thereof, those skilled in the art will undoubtedly come up with numerous modifications and variations in the embodiments and / or aspects shown herein, all of which may be accomplished without departing from the spirit and scope of the present disclosure. Accordingly, the apparatus and method embodiments shown and described herein are for illustrative purposes only, and unless otherwise specified in the following claims, the scope of the present disclosure extends to all processes, apparatus, and / or structures that provide various benefits and / or features of the present disclosure (which benefits may include, but are not limited to, accommodating misalignment of a shaft(s) relative to a housing and / or shaft seal assembly, whether the misalignment is angular, radial, and / or axial, and / or configuring a shaft seal assembly to create a pressurized fluid barrier between rotating and non-rotating elements).

[0097] Although the apparatus and methods have been described herein with reference to preferred aspects and specific examples, it is not intended that the scope be limited to the illustrated embodiments and / or aspects, as the embodiments and / or aspects described herein are intended in all respects to be illustrative and not restrictive. Accordingly, the apparatus and methods shown and described herein should not be construed as in any way limiting the scope of the present disclosure, unless so stated in the following claims.

[0098] Although some of the drawings are drawn to scale, any dimensions given herein are for illustrative purposes only and in no way limit the scope of the present disclosure, unless otherwise specified in the following claims. It should be noted that the apparatus and method are not limited to the specific embodiments shown and described herein, but rather the scope of the inventive features according to the present disclosure is defined herein by the claims. Modifications and variations from the described embodiments will occur to those skilled in the art without departing from the spirit and scope of the present disclosure.

[0099] Various features, components, functions, advantages, aspects, configurations, method steps, etc. of the devices and methods may be used alone or in combination with one another depending on the suitability of such features, components, functions, advantages, aspects, configurations, method steps, etc. Thus, an almost infinite number of variations of the present disclosure exist. Modifications and / or substitutions of one feature, component, function, aspect, configuration, method step, etc. for another in no way limit the scope of the present disclosure, unless otherwise specified in the following claims.

[0100] The present disclosure extends to all alternative combinations of one or more individual features described above that are apparent from the context and / or drawings and are inherently disclosed. All of these various combinations constitute various alternative aspects of the present disclosure and / or its components. The embodiments described herein describe the best known modes of carrying out the apparatus, methods, and / or components disclosed herein and enable those skilled in the art to utilize this best mode. The claims include alternative embodiments to the extent permitted by the prior art.

[0101] Unless otherwise specified in the claims, it is in no way intended that any process or method set forth herein be construed as requiring that the steps be performed in a particular order. Thus, unless a method claim actually recites the steps following a certain order, or unless the claim or specification otherwise specifically states that the steps are to be limited to a particular order, no order is intended to be inferred in any respect. This also applies to the plain meaning derived from any possible implicit basis, grammatical construction or punctuation, including, but not limited to, logical matters to the construction of steps or operational flow, number or type of embodiments described herein. [Explanation of symbols]

[0102] Symbols in Figures 1 to 12: 1-axis 2 Fixed stator 2a Fixed stator (partial line) 3 Labyrinth Seal 3a Rounded surface 4 Floating Stator 5 Fluid return 6 Shaft seal clearance 7 First O-ring 8 Anti-rotation pin 9. Ventilation 10 Anti-rotation groove (floating stator) 11 Spherical boundary surface 12 Anti-rotation pin 13 Second O-ring 14 Labyrinth seal pattern groove 15 First O-ring passage 16 Cavity for anti-rotation device (fixed stator) 17 Labyrinth seal shaft surface 18 Floating stator axial surface 19 Second O-ring passage 20 First gap between floating stator and fixed stator 21 Secondary gap between floating stator / fixed stator 22 Throttle groove 23 labyrinth pattern angle direction groove 24 Sleeve 25 Shaft seal assembly 26 Throttle (centering skate) 27 Floating stator annular groove 28 Labyrinth Seal Passage 29 Floating stator passage 30 Case 31 Misalignment angle 32 Bearings and bearing cavities 33 Assembly bolt 34 Container Wall 40 Pressure balanced shaft seal assembly 42 Labyrinth seal inner surface 44 Floating stator inner surface 46 Pressure-balanced annular passage 47a first radial boundary surface 47b Second radial boundary surface 48 Fixed stator annular groove 48a: radial inner surface of annular groove Symbols in Figures 13 to 15A: 10 Axis 18 Bearing separator 19. Cabinet 20 Rotors 30 Stator 31a Stator 31 Fixed stator Aisle 40 Aisle 40a 50 Spherical surface 51 Spherical surface 52 Gap 60 Friction Seal 61a Flange type unit 80 center point 99 Conduit 100 fluid 101 Pin 102 Annular recess Symbols in Figures 16 to 21B: 10 Shaft seal assembly 12 Axis 14 Fasteners 20 Fixed stator 20a Fixed stator seal groove 21 Main body 22 face plate 22a Faceplate pin recess 22b Face plate seal groove 24 Entrance 26 Annular recess 28 Seal 30 Floating Stator 30a Floating Stator Seal Groove 32 Radial outer surface 33 First pin recess 34 pin 35 Second pin recess 35a Second pin recess enlarged portion 37 Floating stator angle groove 38 Concave 40 Sealing member 42 Recess 44 Radial Hole 44a Radial hole inlet 44b Radial hole exit 46 Radial inner surface 48 Convex 100 Seal assembly 102 O-ring 104 Fasteners 105 Received 106 Aperture 108 pins 110 First stator 110a Upper part 110b lower part 111 Annular recess 112 Concave 112a Shelf 113 Small hole 114 Inner member 114a Entrance 116 Outer member 116a First stator recess 120 Second Stator 121 Second stator annular recess 122 Main body 122a Convex 122b Convex shelf 123 Second stator recess 124 Second stator inlet 125 Internal passage 126 Main body shelf 127 Axial recess 128 Access Plate 128a Shoulder 128b Axial hole 129 Annular Space 130 Throttle member 131 Throttle member annular recess 132 The First Wall 132a first wall axial protrusion 133 Middle part 133a Radial passage 134 The Second Wall 134a Axial projection 136 Throttle member passage

Claims

1. 1. An annular seal assembly, comprising: a. a first stator having a concave surface formed on a radially inner portion; a second stator disposed within the first stator, the second stator being formed with a convex surface on a radially outer portion, the concave surface of the first stator and the convex surface of the second stator forming a hemispherical interface between the first stator and the second stator, and the second stator being formed with an internal passage on a radially inner surface; c. a throttle member disposed within the internal passage of the second stator; the throttle member is formed with an intermediate portion between a first wall and a second wall, the periphery of the intermediate portion being smaller than the periphery of the first wall and the periphery of the second wall. Annular seal assembly comprising:

2. and an access plate selectively engageable with an axially directed surface of the second stator, the access plate and the second stator cooperating to define a portion of the internal passage. The annular seal assembly of claim 1 .

3. The first stator further includes an inlet extending from a radially outer surface of the first stator to the concave surface.

3. The annular seal assembly of claim 2.

4. The second stator further includes a second stator inlet extending from a radially outer surface of the second stator to the inner passage.

4. The annular seal assembly of claim 3.

5. The throttle member further includes a radial passage within the intermediate portion, the radial passage extending from a radially outer surface of the intermediate portion to a radially inner surface of the intermediate portion.

5. The annular seal assembly of claim 4.

6. The throttle member further comprises a plurality of radial passages within the intermediate portion, the plurality of radial passages being equally distributed around an outer periphery of the intermediate portion.

6. The annular seal assembly of claim 5.

7. The concave surface further includes a shelf formed therein.

3. The annular seal assembly of claim 2.

8. The convex surface further comprises a convex shelf.

3. The annular seal assembly of claim 2.

9. The second stator includes: a. a main body, the internal passageway being formed within a portion of the main body; b. a main body shelf extending axially outwardly from said main body; the access plate is disposed adjacent a radially inner surface of the main body shelf.

3. The annular seal assembly of claim 2.

10. The first stator is further defined as consisting of an upper portion and a lower portion. The annular seal assembly of claim 1 .

11. The annular seal assembly is further defined as bifurcating along a diameter of the annular seal assembly. The annular seal assembly of claim 1 .

12. The throttle member further includes a throttle member annular recess formed in an axially outer surface of the second wall, an O-ring being disposed within the throttle member annular recess. The annular seal assembly of claim 1 .

13. The concave surface further includes an annular recess formed therein, and an O-ring is disposed within the annular recess. The annular seal assembly of claim 1 .

14. The second stator is movable relative to the first stator about the hemispherical interface such that a longitudinal axis of the second stator may be misaligned with a longitudinal axis of the first stator. The annular seal assembly of claim 1 .

15. The access plate is further defined as being selectively threadably engageable with the second stator. The annular seal assembly of claim 1 .

16. 1. An annular seal assembly, comprising: a. an annular stator having a concave surface formed on a radially inner portion; b. a second stator disposed within the first stator, the second stator being formed with a convex surface on a radially outer portion, the concave surface of the first stator and the convex surface of the second stator forming a hemispherical interface between the first stator and the second stator; c. an access plate selectively engageable with the second stator, the access plate and the second stator cooperating to define an internal passage on a radially inner surface of the access plate and the second stator; d. a throttle member disposed within the internal passage; the throttle member is formed with an intermediate portion between a first wall and a second wall, the first wall and the second wall extending radially beyond the intermediate portion. Annular seal assembly comprising:

17. The first stator further includes an inlet extending from a radially outer surface of the first stator to the concave surface. The annular seal assembly of claim 16.

18. The second stator further includes a second stator inlet extending from a radially outer surface of the second stator to the inner passage. The annular seal assembly of claim 17.

19. The throttle member further includes a radial passage within the intermediate portion, the radial passage extending from a radially outer surface of the intermediate portion to a radially inner surface of the intermediate portion. The annular seal assembly of claim 18.

20. The throttle member further comprises a plurality of radial passages within the intermediate portion, the plurality of radial passages being equally distributed around an outer periphery of the intermediate portion. The annular seal assembly of claim 19.

21. The concave surface further includes a shelf formed therein. The annular seal assembly of claim 16.

22. The convex surface further comprises a convex shelf. The annular seal assembly of claim 16.

23. 1. An annular seal assembly, comprising: a. a first stator having a concave surface formed on a radially inner surface, the first stator configured to be selectively engageable with a housing having an axis extending from the housing and rotatable relative to the housing, the first stator configured to be disposed about a circumference of the axis; a second stator disposed within the first stator around the circumference of the shaft, the second stator being formed with a convex surface on a radially outer portion, the concave surface of the first stator and the convex surface of the second stator forming a hemispherical interface between the first stator and the second stator, the second stator being formed with an internal passage on a radially inner surface; c. a throttle member disposed within the interior passage of the second stator adjacent the outer periphery of the shaft; the throttle member is formed with an intermediate portion between a first wall and a second wall, the first wall and the second wall extending radially beyond the intermediate portion, and the throttle member is movable in at least a radial dimension relative to the first stator and the second stator. Annular seal assembly comprising:

24. and an access plate selectively engageable with an axially directed surface of the second stator, the access plate and the second stator cooperating to define a portion of the internal passage. The annular seal assembly of claim 23.

25. The first stator further includes an inlet extending from a radially outer surface of the first stator to the concave surface. The annular seal assembly of claim 24.

26. The second stator further includes a second stator inlet extending from a radially outer surface of the second stator to the inner passage. The annular seal assembly of claim 25.

27. The throttle member further includes a radial passage within the intermediate portion, the radial passage extending from a radially outer surface of the intermediate portion to a radially inner surface of the intermediate portion.

27. The annular seal assembly of claim 26.

28. The throttle member further comprises a plurality of radial passages within the intermediate portion, the plurality of radial passages being equally distributed around an outer periphery of the intermediate portion.

28. The annular seal assembly of claim 27.

29. The concave surface further includes a shelf formed therein. The annular seal assembly of claim 24.

30. The convex surface further comprises a convex shelf. The annular seal assembly of claim 24.

31. 1. A method of sealing an area between a housing and a shaft extending from the housing, the method comprising: a) engaging a first stator with the housing, the first stator being formed with a concave surface formed on a radially inner portion, a second stator being disposed within the first stator, the second stator being formed with a convex surface on a radially outer portion, the concave surface of the first stator and the convex surface of the second stator forming a hemispherical interface between the first stator and the second stator, and the second stator being formed with an internal passage on a radially inner surface; b. allowing the second stator to move relative to the first stator about the hemispherical boundary surface; c) disposing a throttle member disposed within the interior passage of the second stator, the throttle member being formed with an intermediate portion between a first wall and a second wall, the outer periphery of the intermediate portion being smaller than the outer periphery of the first wall and the outer periphery of the second wall; d. allowing the throttle member to move radially within the internal passage a predetermined amount relative to the first stator and the second stator; e. allowing the shaft to move axially relative to the throttle member and the first and second stators through a circumferential gap between an inner surface of the throttle member and an outer surface of the shaft. A method comprising:

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