CA2056285C - Balanced mechanical seal assembly - Google Patents

Abstract

A mechanical seal assembly is disclosed in which the seal faces of the primary seal members remain essentially perpendicular to the shaft of the equipment regardless of any misalignment. A sleeve is mounted on the shaft, providing a support structure to align all primary seal member faces regardless of loading. The primary seals are biased toward the support structure, by the combination of net hydraulic pressure at the mated seal faces plus steady bias from a biasing source. A piston area is defined on the rear of each primary seal member. Each piston area is equal to a major portion of the associated primary seal face contact area. Another embodiment further includes a gland mounted to the equipment concentrically to the equipment shaft and an axially floating annular flow ring located within the gland. The ring supplies a fluid flow channel associated with the shaft vanes.

Description

BALANCED MEGFLANTGAL SEAL AS3EMBLy Field of the Inv -nt; r,n This invention relates to mechanical seals, balanced mechanical seals, and a flow ring for acceleration of barrier fluid within the seal.
Hackaround of the Invention Mechanical seals utilize relatively rotating and contacting seal faces, i.e., mating seal faces of a stator ring fixed to a gland and of a rotor ring fixed to the shaft of a rotary equipment, to isolate and seal a pressurized liquid. i.e., the process fluid, along the equipment shaft. To cool the seals and to aid in preventing any passage of process fluid across the seal faces, a second pressurized liquid, i.e., a barrier fluid, is often introduced to the seals on the rear side of the seal faces opposite that in contact with the process fluid. Typically, vanes are formed on the rotating shaft to accelerate the barrier fluid flowing between the shaft and gland. Springs normally bias the seal faces together.

_2_ In balanced seal arrangements the pressurized fluids are also applied to piston axeas defined on the rear sides of the seal members opposite the seal faces to aid in closing the seal faces. In general, it is desirable to have the piston area associated with the fluid having the higher pressure to be less than 100% and preferably about 70% of the contact area of the seal faces.
This relationship minimizes heat generation from the frictional contact of the seal faces while maintaining a closing force can the seal faces sufficiently high to assure proper sealing. Tt is also desirable to minimize the contact area of the seal faces so as to minimize heat generation as the seal faces rotate relative to each other.
Additionally, when a barrier fluid is employed, a double seal arrangement is often utilized in which the process fluid is confined to one end of the seal and the barrier fluid to the center of the seal with relatively rotating seal faces on either side of the barrier fluid; with the local environment being sealed at the other end of the seal.
Tn one type of balanced double seal in. the priox art both fluids have access to the rear of the respective seal members opposite the seal faces and the desired balance ratio of the piston area to the seal face contact area is achieved by providing O-rings sl~.dable in their O-ring grooves behind the respective seal faces of the seal members. The O--rings slide in the grooves to psrmat applica~~.on of fluid pressure from the fluid having the highest pressure to the appropriate piston areas on the sides of the seal members opposite the seal faces> Springs biasing the seal faces together are located within the seal on either side of the seal faces and may be exposed to either or both of the process and barrier fluids. This arrangement has significant limitations. First, since the inner and oute r diameters of the O-rings define the balance pressure points for the respective fluids, the radial contact dimension of the seal faces must be sufficiently large to account for the thickness of the 0-rings.
This limits the design of the seal faces for which minimum contact area is desired. Second, if the O-rings do not slide as intended in their grooves, the balance pressures will not be achieved as intended. Additionally, the springs, exposed to the process and barrier fluids, are subject to contamination and corrosion.
It is therefore an object of the present invention to provide a mechanical seal assembly which overcomes the deficiencies of the prior art.
It is another object of the present inventian to provide a balanced seal assembly where tie balance pressures are not effected by O-ring movement.
Tt is another object of the present invention to provide a double balanced Bauble seal assembly where the balance pressures are determined by fired piston areas defined on rear surfaces of the mating primary seal rings.

It is yet another object of the present invention to provide a balanced seal assembly in which the primary seal members remain squared to each other and to the rotating shaft regardless of shaft runout or endplay.
It is a further object of the present invention to provide a seal assembly having a floating flow ring which optimizes acceleration and 1o delivery of barrier fluid within the barrier fluid chamber of the seal assembly regardless of shaft anomalies.
These and other objects are met by the presently disclosed invention. In one aspect of the invention, the seal assembly isolates the sealing process from any misalignment between the shaft of the equipment being sealed and the equipment itself, 2o i.e., between the shaft and a plane perpendicular to the endface of the equipment stuffing boa upon which the seal gland is mounted.
The equipment to be sealed has a relatively rotary part and a relatively stationary housing part, each port being concentric to a central axis of the equipment to be sealed. The interior of the stationary equipment comprises a central annulus which defines a stuffing box through which the shaft of the stationary equipment extends.

In a preferred embodiment, the~seal assembly has relatively rotatable annular primary seal members for sealing and separating process and barrier fluids respectively on radially inner peripheries of the primary seal members, the seal members defining respective annular, radially eztending, opposed seal faces therebetween contacting each other over a predetermined contact area. A shaft sleeve having a flange at one end is provided in this embodiment, and the seal members are mounted relative to the sleeve between a flange at one end of the sleeve and springs at the other end of the sleeve. A respective secondary seal contacts a respective one of the primary seal members on the rear sides thereof at positions spaced azially from and opposite the seal faces, at fined diameters of the primary seal members, prevent passage of fluid~azially along the seal members.
The above primary seal members form a first and second pair of primary seal members and the associated secondary seals form a first and second pair of secondary seals, and form inboard and outboard seals with a sealed barrier fluid chamber thereinbetween.

~0~~~~~
A gland is mounted on the equipment nominally concentrically to the shaft and two stationary ones of the primary seal members are resiliently and slideably mounted thereto. The other two primary seal members are mounted on the sleeve for rotation with the shaft, the outbaord one of which being slideably mounted and the inboard one being in abuttment with the sleeve flange. With the springs biasing the primary seal members together and ZO into the flange, the primary seal members remain aligned relative to the flange without regard to shaft endplay and runnout.
In another aspect of the invention, a double balanced double seal is disclosed in which a fixed and predefined piston area is defined on the rear side of each primary seal member without regard to secondary seal location or thickness.
In a preferred embodiment, the piston areas are axially aligned (i.e., coaxial3 with and smaller than the contact area of the seal faces. Each such piston area forms a predetermined area preferably equal to a major portion of the contact area. One of the piston areas extends radially inwardly in fluid communication with the inner periphery of the primary seal members and the other of the piston areas extends radially outwardly in fluid communication with the outer periphery of.~he seal members. The axially outer one of the piston areas serves as a piston area for the barrier-fluid and the other axially inner one of the piston areas serves a~ a piston area for the pxocess fluid.

Tn various embodiments, the contact areas of the first and second pairs of seal faces are equal.
One axially inner seal member of the first pair of primary seal members is positioned at the opposite end of the seal assembly from the one axially outer seal member of the second pair of seal members, each having its rear side facing away from the others of the first and second primary seal members, with the piston area thereof extending radially inwardly and communicating with the inner periphery of all of the primary seal members; the piston areas of these one seal members of the first and second pairs of primary seal members being equal. Preferably the sadially inner periphery of each of the primary seal members is in communication with the barrier fluid.
Advantageously, a seal assembly according to the present invention seals an equipment shaft without regard to misalignment between the shaft and equipment, and achieves pressure balance by virtue of the geometry of the parts, providing fixed, predetermined piston areas on the sides of the primary seal members opposite the seal faces without reliance on any movable parts (such as O-rings) which may be subject to wear or malfunction. An individual piston area is exposed to only one of the fluids.
Further, the contact area of the seal faces may be optimized without any limitation imposed by the size of the 0-rings defining the balance pressure points.
According to anothbr feature of the invention, the springs biasing the seal faces are positioned at one end of the peal assembly and are not exposed to either process or barrier fluids. Advantageously, these springs can be observed as a measure of seal _g_ face wear. Additionally, the spring load is generally unaffected by misalignment of the seal assembly and equipment shaft on which the seal assembly is mounted. Advantageously, as well, pressure balance of the seal faces is achieved in both directions with no relative motion of the seal assembly parts required to achieve the balance.
Furthermore, because the invention makes possible design of seal faces having small contact area. heat generation in operation of the seal assembly is minimized.
In yet another aspect of the invention, these features and advantages are further exploited in an arrangement for optimizing delivery of the barrier fluid to the parts to be contacted therewith, in which the facing rear ends of the non-rotatable stationary primary seal members abut a respective axial side of an axially floating, anti-rotation providing, annular flow ring mounted concentrically to the shaft. The ring is generally annular and defines an internal flow path or flow channel by having an interior circumferential floor portion at a first inner diameter bordered by sidewalls thereof which terminate at a smaller inner diameter only slightly greater than the local outer diameter of the shaft sleeve thereat.
In a further aspect, the present invention provides a double mechanical seal assembly having a gland for fixed attachment to a housing of equipment having a rotary shaft means, the shaft means comprising a shaft which is subject to endplay and fluid-flow acceleration - 8a -vanes associated with said shaft, said gland having an interior surface for non-rotatably receiving a pair of annular primary seal members having seal faces which mate with a respective seal face of a second pair of annular primary seal members which are non-rotatably mounted to said shaft means, said primary seal members forming two pairs of mated seal faces defining a sealed barrier-fluid environment, a first pair of said mated seal faces sealing process fluid along said shaft means in a process-fluid environment, said gland having a pair of ports extending radially therethrough and each port having a mouth located for opening into said barrier-fluid environment adjacent to said vanes for providing barrier-fluid flow thereat in a direction of rotation of said shaft means when said gland is mounted to said equipment concentrically to said shaft, the seal comprising an axially floating, annular flow ring having an outer circumferential surface for mounting to said gland interior adjacent to said port mouths and axially between said primary seal members associated with said gland, an interior of said floating ring comprising an obstructed flow channel, said floating ring having sidewalls extending radially inwardly to an inner diameter of said floating ring, said flow channel defined along an inner circumferential surface of said floating ring axially located between said sidewalls, said floating ring further comprising a pair of passages extending radially through said outer and inner circumferential surfaces, said ring interior further including a dam located between said passages, said dam blocking fluid flow between said passages in a first rotational direction in said flow channel, said passages floatingly communicating with ones of said gland port mouths to facilitate flow of barrier fluid through said ports, passages, and flow channel, in a second rotational direction, and mounting means for non-rotatably mounting said floating ring and said primary seal members - 8b -associated with said gland to said gland, said mounting means permitting axial travel of said gland-mounted primary members and said floating ring to accommodate axial shifting of said shaft means while sealing barrier fluid flow in said barrier-fluid environment, whereby said axial travel of said floating ring maintains said flow channel located adjacent to said vanes regardless of shaft endplay while said mated seal faces remain mated.
In a further aspect, the present invention provides a double balanced double mechanical seal assembly having a predetermined pressure balance for sealing process fluid in a first fluid environment at an inboard seal within a stuffing box of equipment concentric to a shaft of said equipment and having an outboard seal for sealing a second fluid environment between itself and said inboard seal, the seal assembly comprising relatively rotatable primary seal members defining said inboard and outboard seals and mounted substantially concentrically to said shaft, a plurality of secondary seals sealing said primary seal members with respect to said equipment within said seal assembly for sealing said first fluid environment from said second fluid environment, wherein each said primary seal member has a radial seal face side extending between an inner and outer diameter thereof defining a respective radially extending sealing face, said seal faces of a first pair of said primary seal members being mated to form said inboard seal over a first primary seal face contact area extending between first inner and outer primary seal face contact area diameters, said seal faces of a second pair of said primary seal members being mated to form said outboard seal over a second primary seal face contact area extending between second inner and outer primary seal face contact area diameters, bias means located only outside of said first fluid environment and applying a biasing force only against primary seal members forming said outboard one of said seals, thereby biasing all of said seal faces in one direction, each said primary seal member comprising, a side opposite said radial seal face side thereof, each said opposite side extending between an intermediate diameter thereof and one of said inner and outer diameters thereof, and comprising a fixedly predetermined generally radially extending piston area associated therewith, each said primary seal member piston area being defined as extending radially between said intermediate diameter of said primary seal member with which it is associated and one of said inner or outer primary seal face contact area diameters, and each said piston area being a predetermined fixed area equal to a major portion of said contact area, independent of thickness or location of said secondary seals.
In another aspect, the present invention also provides a in a mechanical seal assembly for mounting over the shaft of equipment to be sealed, the seal assembly having a sleeve for mounting concentrically and longitudinally parallel to said shaft, first and second pairs of primary relatively rotatable seal members, the rotatable seal members mounted on said sleeve, each said pair having first and second radially extending opposed seal faces forming a seal therebetween by contacting each other over a predetermined contact area, a method for isolating each said seal from misalignment between the equipment shaft and the equipment, the method comprising the steps of providing a flange at one end of said sleeve with a flange surface extending radially outwardly at a right angle to the longitudinally extending sleeve;
assembling said primary seal members serially on said sleeve in abutting relation and with a non-seal-face side of an inboard one of said primary seal members abutting said flange surface, with said inboard one and said primary seal member furthest from said inboard one - 8d -connected to said sleeve for rotation therewith, the other said primary seal members adapted for connection to a stationary structure; and maintaining uniform biasing across all seal faces regardless of any said misalignment, by providing a biasing means connected to said sleeve only at the end of said sleeve opposite said flange end in contact with said primary seal member furthest from said inboard member, thereby biasing said primary seal members with respect to and only in one direction toward said flange.
In a further aspect, the present invention provides a mechanical seal assembly for retaining process fluid within equipment, the equipment having a relatively rotary part and a relatively stationary housing part, the interior of said housing part forming a stuffing box, each said part being concentric to a central axis of said equipment, said housing part for mounting of said seal assembly concentrically to said equipment central axis, said rotary part being axially shiftable under load between a first and second axial position relative to said housing part, said seal assembly having a first and a second pair of primary seal members, each said pair having a rotary primary seal member associated with said rotary part and a stationary primary seal member associated with said stationary part, said members of each said pair having surfaces defining relatively rotatable seal faces which mate to define an associated seal face contact area, said associated contact area of said first pair defining an axially inboard seal proximally associated with said stuffing box and which is fluidly loaded thereat and said contact area of said second pair forming an outboard seal which is fluidly loaded thereat and which is outboard from said inboard seal, said seal assembly having a central axis and said inboard and outboard seal being formed concentric to said seal assembly axis, said seal assembly further comprising - 8e -biasing means for applying axial bias to said seal faces, and a support sleeve for mounting concentrically over said rotary part, said support sleeve havincr an inboard support structure extending radially and essentially 5 perpendicular to said rotary :part, said prirriary seal members being mounted relative to said suppc~rt sleeve such that said seal faces are held essentially perpendicular to said rotary part, with one of said rotary primary sea:1 members and both of said stationary 10 primary seal members being axially slidably mounted relative to said support sleeve for sliding toward said support structure according to bias from said biasing means, and said support sleeve supporting said biasing means and said sl:idable ones of said primary seal members 15 such that said bias from said biasing means and net fluid load from said loaded inboard and outboard seals is persistently and evenly applied to said inboard and outboard seals, transmitted through said primary seal members between said biasing means and said support 20 structure, regard:Less of shifting of said rotary part between said first and second axial positions.
According to a further aspect of the invention, there is provided a mechanical seal assembly comprising a 25 first primary seal member associated with a stationary structure of equipment to be sealed and a sE:cond primary seal member associated with a shaft of said equipment, said equipment having a central axis and being of the type having a stuffing box through which the shaft 30 extends axially a:Long said central axis, thE: seal members defining relative:Ly rotatable seal faces which mate to define a radial contact area therebetween for sealing a process fluid within said equipment, the seal assembly comprising a gland comprising a stationary :structure for 35 stationary mounting to said equipment concentrically to said shaft, said gland defining a central annulus for receipt of said shaft, and isolation means f=or isolating _ 8f _ misalignment between said shaft and said central axis from said seal faces such that said seal faces generally remain mating and remain perpendicular to said shaft, regardless of any said misalignment, said isolation means 5 comprising a sleeve assembly :Eor mounting on said shaft, said sleeve assembly :inc:Luding a sleeve with a flange at one end of said sleeve, wherein said first and second primary seal members form a first seal at their mating seal faces, and a third primary seal member mounted to 10 said gland and a fourth primary seal member resiliently mounted to said s:Leeve form a second seal at their mating seal faces, said first primary seal member and said third primary seal member each being sealed by a respective secondary seal to said gland and said seconc. primary seal 15 member and said fourth primary seal member each being sealed by a respective secondary seal to said sleeve, said sleeve sealed by another secondary seal to said shaft, wherein said first primary seal member in cooperation with said second primary seal member and 20 associated secondary seals seal process fluid from within said equipment from passage to said second ~:eal, wherein said first and second seals form a chamber for receipt of a barrier fluid, said seal assembly also including biasing means mounted at the other end of said sleeve, 25 said sleeve assembly and biasing means maintaining uniform biasing across all said seal faces regardless of any said misalignment, said biasing means including a plurality of springs and said secondary primary seal member being axia:Lly slidably mounted on said sleeve, 30 said first and second primary seal members being mounted under uniform compression from said springs and transmitting said compression from said springs to said flange, and wherein said compression springs are located circumferentially about only one end of said sleeve 35 assembly concentrically to said shaft, said isolation means preventing flexure of said springs regardless of any said misalignment.

_ g ~~ _ Various embodiments of the shaft or sleeve include pump vanes for accelerat:Lon of the barrier fluid as the shaft rotates. AdvantagE=ously in this embodiment, the ring floats axially with travel of the non-rotatable 5 stationary members. This floating maintains the flow channel centered over the pumping ~p5~~8~
vanes so as to optimize delivery of the cooling barrier fluid to the axially shifted seal faces in the event of shaft endplay.
Fluid flow in one portion of the defined flow channel is obstructed by a dam formed on the ring interior. The ring Further defines a pair of fluid ports, serving as a fluid inlet port or fluid outlet port according to the direction of shaft ZO rotation. Each port extends radially through the ring circumference and terminates at the ring interior as the port opens into the defined flow channel. The unobstructed portion of the Flow channel provides a barrier-fluid flow path from the inlet port to the outlet port in a desired fluid-flow direction, while the dam prevents fluid flow in the opposite direction.
The dam is formed by a pair of flanges which extend radially inwardly from a common origin on the outer circumference of the ring. Each flange defines a respective circumferential opening extending radially through the ring. The inlet and outlet ports are each respectively formed as a radial circumferential opening joining a respective one of the flange-defined radial circumferential openings.
In operation, at the inlet port. the associated flange directs fluid flow inwardly between the rotating shaft and the unobstructed flow channel and at the outlet port the associated flange directs the accelerated fluid outwardly out of the flow channel.

-lo- ~Da6~d~
The outer circumference of the flow ring includes anti-rotation bosses which engage the anti-rotation notches of the facing ends of the abovesaid non-rotatable members. An anti-rotation lug secures the ring to the seal gland. Thus the notched members and the flow ring are secured against rotation, and alignment of the inlet and outlet ports of the flow channel with respective mouths of radial inlet and outlet ports of the gland is thereby assured. The seal inlet and outlet ports couple with the ring inlet and outlet ports essentially tangentially to the shaft central axis. The inner diameter of each of the port mouths is greater than the inner diameter of the port associated therewith so that fluid flow is facilitated even with axial floating of the ring.

-11- ~~~6~~~
Brief IJescription Of The Drawing These and other features and advantages of the present invention will be more fully understood by reference to the following detailed description in conjunction with the attached drawing in which like reference numerals refer to like elements and in which:
FIG. 1 is a front elevation view of a mechanical seal assembly of the invention.
FIG. 2 is an enlarged sectional view of the invention of FIG. 1 taken at line 2-2.
FIG. 2A is a fragmentary sectional view of the invention of FIG. 1 similar to FIG: 2, taken at a point rotated 90° from FIG. 2.
FIG. 2B is an enlarged sectional view of the invention of FIG. 1, taken at line 2B-2B of FTG. 2A.
FIG. 3 is an exploded perspective view of the invention of FIG. 1.
FIG. 9 is an enlarged fragmentary view of a portion of the sectional view of FIG. 2.
FIG. 5 is a side view of a flow ring of the invention.
FIG. 5A is a cross-sectional viow of the ring of FIG. 5 takan at line 5A-5A.

FIG. 5B is a perspective view of the ring of FIG . 5 .
FIG. 5C is a sectional view of an alternative embodiment of the invention of FIG. 2 with ring 120 installed.
FIG. 6 is a sectional view of an embodiment of the seal of FIG. 1 taken at line 2-2 with a flow ring installed.

Detailed Description of Preferred Embodiments Referring now to FIGS. 1-3. a mechanical seal assembly 10 according to the invention is mounted on a pump shaft l2 and is secured to the pump housing l4 by bolts 16. Seal assembly l0 extends partially into the stuffing box 18 of the pump housing.
The seal 10 includes a sleeve 20 adjacent shaft 12. At the inboard end of the sleeve 20, i.e., the end inserted into the stuffing box l8, a groove 22 on the inner periphery of.sleeve 20 receives an O-ring 24 adjacent shaft 12 to prevent process fluid from passing from the pump between sleeve 20 and shaft 12. Sleeve 20 has a stepped construction at its inboard end and thus defining a flange 26, the flange having an outer diameter smaller than the inner diameter of the stuffing box 18 and having an outwardly facing wall 28 squared at right angles to the inner surface of sleeve 20 adjacent shaft 12. A step 30 is provided axially outwardly of flange 26 and has a diameter greater than that of the major portion of sleeve 20 but smaller than that of flange 26. A groove 32 in the outer surface of step 30 receives an 0-zing 34. A
plurality of bosses 36 ire pravided adjacent step 30 about the circumference of the sleeve. In the embodiment described, three bosses equally spaced are provided about the sleeve: Referring to FIG. 3, adjacent the outer end of the sleeve, a plurality of circular apertures extend through the sleeve hawing three large apertures 38, three smaller apertures 39;
and three smaller apertures 40, the apertures alternately equally spaced about the czrcumference of the sleeve.

_14_ ~0~~~~5 A rotary seal member 42 is mounted on the inboard end of sleeve 20. The seal member 42 has a relatively wide seal portion 44 having an axially outwardly facing seal face 46. Seal member 42, on the seal portion 44 inner diameter, has a plurality of notches 48 engaging the bosses 36 on sleeve 20 and locking the rotary seal member 42 to sleeve 20 for rotation therewith. The outer diameter of rotary seal member 42 is slightly smaller than that of flange 26 of sleeve 20 and is spaced from the inner wall of the stuffing box 18. On the rear side ~f seal portion 44 opposite face 46, the inner diameter of rotary seal member 42 adjacent sleeve step 30 is increased, providing seal member 42 with a step 50 having an inner diameter approximately equal to the outer diameter of sleeve step 30. O-ring 34 in groove 32 of sleeve step 30 seals against the inner diameter of stag 50 of rotary seal 42, such that step 50 is resiliently sealed to and spaced from step 30 thereby. The inner diameter of seal portion 44 of rotary seal member 42 is slightly greater than the local outer diameter of sleeve 20, such that bosses 36 can freely mate notches 48. The axially inwardly facing wall 52 of member 42, opposite seal face 46, is spaced from the end wall 31 of step 30 to permit fluid access therebetween, thus forming piston area ~1 on wall 52. In an alternative embodiment, end wall 31 is employed as a reference surface in stead of wall 28 of flange 26, since it also is perpendicular to the shaft.
A stationary seal member 54 is provided axially outwardly of rotary' seal member 42.
Stationary seal member 54 includes a seal portion 56 _15_ extending from an inner diameter somewhat greater than the outer diameter of sleeve 20 to an outer diameter slightly smaller than the inner diameter of stuffing box 18. A narrow axially inwardly facing seal face 58 extends from the seal portion 56 toward and sealingly engages the seal face 46 of rotary seal member 42. Outwardly of seal portion 56 of stationary seal member 54, a secondary sealing portion 55 is defined by a step 60 at an outer diameter reduced relative to the outer diameter of sealing portion 56 and defining an axially outwardly facing wall 62 on the rear side of sealing portion 56 opposite seal face. 58. As shown in FIG. 3, four equally spaced notches 64 extend radially through the outer end of step 60. In a particular embodiment, the stationary sea1,54 is made of carbon and the rotary seal member 42 is made of silicon carbide.
A second stationary seal member 54' is provided outwardly of the first stationary seal member 54 in reverse orientation, i.e., with the seal face 58° facing axially outwardly. Stationary seal member 54' is identical to stationary seal member 54, and the corresponding portions thereof are designated with the same reference numerals differentiated by a prime designation. The ends of the stationary seal members 54, 54' opposite seal faces 58, 58' contact each other with notches 64, 64' aligned.
Similarly, outwardly of the second stationary seal member 54' a second rotary seal member 42', identical to rotary seal member 42 and reversely oriented relative thereto, is provided, with a seal face 46' contacting the seal face 58' of 2p~~~8~

the second stationary seal member 54°. The portions of the second rotary seal member 42' are designated with the same reference numerals distinguished by a prime designation, as the corresponding portions of the first rotary seal member 42.
A lock ring 66 is mounted on sleeve 20 at the eater end thereof. Lock ring 66. as illustrated in FIGs. 2 and 3, has a radially enlarged outer end having threaded apertures 68 aligned with aper~tuxes 38 For receiving fasteners 69 locking the seal assembly to the shaft l2 for rotation therewith. The enlarged end of lock ring 66 also has threaded apertures 70 aligned with apertures 40 in sleeve 20 for receiving threaded fasteners 71 having cylindrical ends adapted to engage the edges of apertures 40 and axially locate the seal components prior to assembly in a pump. Three additional threaded apertures 72 aligned with apertures 39, equally spaced in the e~cterior of the lock ring, are provided to receive threaded fasteners 73 for securing centering clips 74 to the lock ring 66. A
groove 76 is provided on the inner surface of the lock ring spaced inwardly from the sleeve apertures 38, 39, 40 and the Iock ring apertures 68, 70, 72.
An O-ring 78 is provided in groove 76 to prevent fluid from moving between the outer surface of the sleeve 20 and inner surface of the IpCk ring 66. The inner edge of lock ring 66 is provided with three axially extending protrusions 80 corresponding to the bosses 36 at the ether end of the sleeve 20: Notches 48° in the second rotary seal member engage the protrusions g0 of the lock ring 66, ocking the second rotary seal 42' thereto for rotatzon with the shaft 12 and sleeve 20. between protrusions 80 and apertures 68, 70. 72 lock ring 66 has a step 82 having a diameter corresponding to and slightly reduced from the diameter of step 30 at the other end of the sleeve. Step 82 has a groove 84 receiving an O-ring 86 sealing against the step 50' at the inner diameter of second rotary seal member 42'. The inner diameter of second rotary seal member 42° at the seal portion 44' thereof is slightly larger than the outer diameter of the sleeve thereat. Wall 52' on the rear side of second rotary seal member 42' opposite seal face 46' is spaced from the end wall 31' of lock ring step 82 to permit access by fluid, thus forming piston area A' as shown in FIG. 2, equal to piston area A. A series of axial bores 87 about the inwardly facing wall of lock ring 66 provide pockets for springs 88 bearing against the outer end of the second rotary seal member 42°. Springs 88 bias all seal faces toward flange 26 at the inward or inboard end of sleeve 20.
A seal gland 90 is positioned generally centrally of the seal assembly. Gland 90, as shown in FIG. l, has a plurality of slots 92 about the exterior thereof to receive mounting bolts 16 for mounting the gland and the seal assembly to the pump housing 14. As shown in FIG. 2, an annular groove 99 on the inner side of gland 90 receives a gasket 96 to prevent leakage of fluid between the pump housiing and the gland. The inner diameter of the gland is provided with a pair of axially spaced g~cooves 98, 100 receiving O-rings 102, 104, respectively, overlying and sealing against the steps for stepped walls} 60, 60' of stationary-seal members 54, 54°.

_1~_ 2~~~~8a The a$ially inwardly facing end 99 of the gland is spaced from axially outwardly facing wall 62 of stationary seal member 54 to permit access by the pracess fluid, thus forming piston area 8; and the axially outwardly facing wall 99' of the gland is spaced from azially inwardly facing wall 62' of stationary seal member 54° to permit access by the sealed environmental fluid (e. g., air), thus forming piston area B'.
Steps 60, 60' radially Locate secondary sealing portions 55, 55° of stationary seal members 54, 54° at a smaller outer diameter than the inner diameter of gland 90, and O-rings 102, 104 are selected to resiliently sealingly accommodate this separation. This arrangement takes advantage of the resiliency of the O-rings and provides a means for sealingly maintaining the secondary seal between the gland and stationary members 54, 5~' steps 60, 60' even when shaft 12 is not parallel to the central axis of the gland. Hence. as a result of this separation and the resiliency of O-rings 102, 104, stationary seal members 54, 54' can rock radially to accommodate shaft runout.
Shaft runout can arise from a stressed or warped shaft, far example, and will cause the rotary seal faces 46, 96'. and indeed the entire rotary seal assembly 67, to be eccentric to the gland central axis. By enabling the stationary seal members to rock along with this rat~ry eccentricity; the respective seal face pairs 46, 58, 46', 58' remain in cantact and parallel to each other as well as to wall 28 of flange 26 and perpendicular to the shaft. Thus - lc~ _ the resilient mounting of. the stationary seal members 54, 54' enables all of the adjustment to shaft runout to be isolated to the secondary seals at O-rings 102, 104, and isolated from the main sealing function at the seal faces of the rotary and stationary primary seal members. A
sleeve assembly, comprising the sleeve 20 and the flange 26, serves as an isolation means for isolating misalignment between the shaft 12 and the gland central axis f rom the seal- f aces .
As a result of the foregoing, seal face wear is reduced and the likelihood of oscillation-caused fatigue of the springs which can otherwise occur from continuously accommodating the rocking seal members is eliminated. As well, friction on O-ring 86 sealing the outer rotor ring 42' to r_he sleeve is advantageously reduced.
Referring to FIGS. 2A, 2B, and 3, a lug 106 is placed in one of the aligned sets of notches 64, 64' of stationary seal members 54, 54' and extends into a recess 108 provided on the. inner diameter of the gland, between grooves 98, 100. Lug 106 has a generally square base fitted in notches 64, 64' and a transverse cross bar 107 extending into recess 108 in gland 90 adjacent notches 64, 64'. As shown in FI~:~. 2A, cross bar 107 is spaced from the axially spaced end walls of recess 108, and as shown in FIG. 2B the width of the cross bar is reduced so that only one of it.s sides 107A or 107B contacts one of the sidewalls 108A or 108B of recess 108. C"ross bar 107 and necessarily recess 108 are somewhat wider, circumferentially, than notches 64, 64' whereby lug 106 is retained in position when assembled. Luq 106 locks stationary seal members 54, 54' to gland 90 and secures these seal members against rotation while permitting axial excursions of= the seal members 54, 54' without interference by the gland.

~0~6~8~

As well, gland axially facing walls 99, 99°
are axially spaced at gaps 111, 111' from axially facing walls 62, 62' on the rear sides of sealing portions 56, 56° of the stationary seal members 54, 54°. This clearance further assures that shaft excursions in either azial direction can be accommodated without effecting mating of the seal faces.
Gland 90 is provided with a pair of radial ports 110, 112. These ports open into the interior of the gland between grooves 98, 100. Ports 110, 112 are provided as inlet and outlet ports for a barrier fluid which passes through those notches 64, 64' not containing lug 106.
The exterior surface of sleeve 20 al~lgned with notches 64, 64' and ports 110, 112 preferably is provided with a plurality of axially extending grooves 65 about its circumference. The grooves function as pumping vanes to assist in pumping barrier fluid from one port to the other.
As shown in FIG. 2, on the exterior of the seal about the inner periphery of gland 90 a groove 114 is provided to receive the radially outwardly projecting ends of the centering clips 74.
The centering clips thus assure axial positioning of the gland and centering of the gland and the stationary seals during assembly.
Referring to F'IG, 4, the inboard first pair of primary seal members 42 and 54; defining the first pair of contacting seal faces 46, 58; are adapted to permit the barrier fluid to exert pressure on rear wall 52, opposite seal face 46, and the process fluid to exert pressure on rear wall 6?., opposite seal face 58. By their construction, the rear walls 52, 62 define predetermined, fixed piston areas, piston area A and piston area B, respectively, transmitting net pressure from one of the fluids toward the first pair of sealing faces 46, 58. Each piston area is defined by the extent to which the associated wall 52, 62 overlaps the contact area of the seal faces 46, 58.
Thus, in the case of rotary seal member 42, piston area A of wall 52 extends between the fixed inner diameter of stationary seal face 58 and the fixed diameter of wall 52 at step 50. Similarly, piston area B on wall 62 of stationary seal member 54 extends between the fixed outer diameter of stationary seal face 58 and the fixed diameter of wall 62 at step 60. In the illustrated embodiment, O-ring seals 34 and 102 where they seal against steps 50 and 60, respectively, define the limits of the piston areas relative to the inner and outer diameters of seal face 58 where they seal against steps 50 and 60, respectively. By groper rad'aal location of the steps 50, 60, which receive seal rings 34, 102, the piston area in each direction (piston areas A and B) can readily be designed to achieve the desired percentage of the contact area of the seal faces 46, 58.
As illustrated in FIG. 4, it is possible to design different piston areas for the respective different fluid pressures for a given application.
Thus, in one preferred embodiment; the piston area B
portion of wall 62 of stationary seal member 54 may equal 70% of the contact area of the seal faces 46, 58, diagrammatically indicated by the tick marks at the faces, each mark representing 10% of the contact area, while piston area A, on wall 52 of rotary seal member 42, equals 60% of the contact area of the seal faces 46, 58. If the geometry of step 30 of sleeve 20 and of rotary seal member 42 were changed so that piston area A of wall 52 extended radially outwardly an additional 10% of the contact area of seal faces 46, 58 (i.e., to line AA), piston area A would then also equal 70% of the contact area and would be the same size as piston area B. In the illustrated embodiment, the spring load necessary to overcome O-ring friction on surfaces 50', 60 and 60' and to bias the seal faces is 40-50 psi, and the piston areas A and A' are each chosen to be 60%
(rather than 70%) of the contact area of the contact faces 46, 58 and 46', 58' as will reduce the total closing force accordingly. Ideally, the piston areas are minimized to reduce friction and heat generation while still providing a safety factor to prevent leakage of fluid across the relatively rotating seal faces. The piston areas must be selected to avoid any net force in the opposite direction tending to open the seal faces.
' The piston areas are of fixed and predetermined size, independent of the thickness or location of the associated secondary seals. The seal face contact area associated with the piston areas is also independent of secondary seal thickness, and therefore can be quite small. The structure is double balanced in that the seal assembly will maintain a net hydraulic plus spring closing force across its inboard and outboard seals regardless of _23-pressure fluctuations, or even upon reversal of the order (low to high or high to low) of the pressures being sealed.
The seal is assembled by placing O-ring 24 in groove 22 and O-ring 34 in groove 32. Rotary seal member 42 is then mounted on sleeve 20 with notches 48 engaging bosses 36 on the surface of the sleeve. O-rings 102; 104 are inserted in grooves 98, 100 of gland 90 and statibnary seal member 54 is inserted into the gland with lug 106 in one notch 64 arranged with cross bar 107 in gland recess 108.
Stationary seal member 54° is then inserted into the other end of the gland in abutting relation to the stationary seal member 54 with lug 106 extending into one notch 64' O-rings 78, 86 are then placed in grooves 76, 84 of lock ring 66; and rotary seal member 42° is mounted an lock ring 66 against springs 88. Gland 90 is mounted about the sleeve 20 and the lock ring is positioned on the end of the sleeve 20. Threaded fasteners 71 are tightened in threaded apertures 70 of the lock ring and into the apertures 40 in the sleeve to axially locate the seal components and to define the pressure exerted by springs 88. Centering clips 74 are fastened into the lock ring by threaded fasteners 73 with thezr ends extending into groove 114 of gland 90. The centering clips axially locate the eland and center the gland and stationary seals pending the assembly in a pump housing.
To assemble the seal in a pump, the seal assembly is slid along the pump shaft with seals 92;
54 extending into the stuffing box 18 of the pump '~

_24_ ~~~~,e~
housing 14. dolts 16 are then tightened in slots 92 of gland 90 to secure the seal to the pump housing with gasket 96 interposed between the gland and the housing. The seal assembly is then secured to the shaft 12 by threaded fasteners 69 extending through apertures 68 of the lock ring and 38 of the sleeve to lock against shaft 12. Centering clips 74 are then removed from the seal assembly.
In operation, sleeve 20 rotates with shaft 12 and carries with it rotary seal members 42,, 42° as well as lock ring ib6 and springs 88.
Stationary seal members 54, 54' are held in a non-rotatably stationary position by lug 106 engaging notches 64, 64' and gland 90. Springs 88 bias both pairs of seal Faces 46, 58 and 46', 58' together and toward flange 26 at the other end of sleeve 20.
Process fluid moves between the outer diameter of seal members 92, 54 and the inner diameter of stuffing box 18. Relatively rotatable seal faces 46, 58 seal the process fluid at their stationary/rotary interface (i.e., at the aforesaid seal face contact area), and O-ring seal 102 seals process fluid from passing beyond non-rotatable seal member 54. Process fluid exerts a closing pressure force an seal faces 46, 58 as it exerts pressure an piston area B.
Preferably; piston area B is equal to 70°~ of the contact area of the seal faces 46, 58. Barrier fluid entering through one of parts 110, 112 of gland 90 is sealed on the outer surface of stationary seals 54, 54' by O-rings 102, 104 in gland groaves 98; 100.
Passing through notches 64; 64' to the outer surface of sleeve 20. the barrier fluid exerts pressure on rear walls 52, 52' of rotary seal members 42, 42' at piston areas A and A'. These piston areas are 70%, or in a preferred embodiment 60%, of the cantact areas of the seal faces 46, 58 and ~!6', 58'. Piston area b° on wall 62' on the opposite side from seal faces 58' is radially defined by face 58° at its outer diameter and at step 60' at its inner diameter, and is acted upon at wall 62' by atmospheric or other external fluid pressure passing between the interior of the gland and the outer surface of seals 42', 54°.
Advantageously, the contact areas of the seal faces are not limited by 0-ring size and can be designed to be as small as. feasible to minimize heat generation. Piston areas A, A' of the rotary seal members 42, 42', where pressure from the barrier fluid is applied, can each be somewhat smaller than piston area B of stationary seal member 54, where pressure from the process fluid is applied to accommodate the sealed pressure difference. Thus the size of the piston areas can be adjusted independently of each other as needed. Of particular significance, such adjustment is made so that net farces closing the seal faces always are directed toward the flange at the end of the sleeve. The springs 88 provide an initial bias toward the flange, and with process fluid exerting farce on wall 62 of stationary seal 59, process fluid pressure further biases the assembly toward the flange. As barrier fluid pressure is applied at piston areas A and A' inwardly fromr~each end of the assembly with no net force in either direction, the spring farce and any process fluid pressure at piston area B and the seal environment net pressure at P', if any, always produces a net force toward the flange:

Advantageously, the seals at faces 46, 58, 46' 53° are not effected by pressure fluctuations between process and barrier fluid. The springs and the pressures at piston areas B, B° supply a net closing force on the seal faces, regardless.
Therefore such fluctuations do not cause shifting of the seal faces relative to O-rings 34, 202, and so there is no risk of "hang-up" of the ~-rings which would unbalance the piston areas (if the piston areas were defined by the O-rings).
Advantageously, there is no axial motion of the seals relative to the springs; thus, constant spring pressure is applied regardless of axial excursions of the shaft. Any radial shaft misalignment has no effect on the springs since the springs bias the assembly against a squared end and the stationary seal members are resiliently mounted and can adjust accordingly with respect to the sleeve, and thus no spring flexure is required if such radial misalignment should occur. Specifically, if the shaft is not square to the stuffing box, the stationary members 54, 54' will rock accordingly relative to gland 90 while they and the rotory seal members 42, 42' remain squared to ~acta other, flange 26, and shaft 12. Because the springs are located outside of the pump and gland, they are not subject to corrosion or contamination from either the process or barrier fluids. Additionally, seal face wear can be judged by observing the length of the springs.
Advantageously, there is no axial motion of the seals relative to the springs; thus, as the sleeve moves with the shaft, constant spring pressure is applied regardless of axial excursions of the shaft.

Notwithstanding the foregoing features and advantages, pumping efficiency of vanes 65 at inlet and outlet ports 110, 112 will diminish as axial excursion of the shaft shifts .the vanes away from the fixedly located ports. Therefore, in an alternative preferred embodiment shown in FIGS. 5-6, an annular flow ring 120 is provided which defines a flow path or channel 121.
Ring 120 optimizes delivery of vane-accelerated barrier fluid flowing through ports 110, 112 along the surface of sleeve 20 and to and from the mated seal faces 46, 58, 46', 58' to be cooled therewith regardless of shaft excursions.
As will be appreciated from the drawings, one embodiment of ring 120 is shown in side view in FIG..S
and an alternative embodiment of ring 120 is shown in FIG. 5A.
Annular ring 120 is nonrotatably mounted on the gland concentrically to the shaft. In particular, the ring has an outer circumferential surface 122 at an outer diameter slightly less than the inner diameter of the adjacent interior surface 124 of gland 90 receiving the ring thereat. The ring has axial sidewalls 126, 126', each of which is provided with an axially outwardly extending flange or boss 128, 128'. In this embodiment, the ends of primary seal members 54, 54' include at least one of the aforesaid notches 64, 64', and these notched ends abut a respective one of -sidewalls 126, 126' with a respective notch 64, 64' mated with a respective flange 128, 128' for non-rotatably mating the seal members to the gland via the ring. The ring sidewalk 126, 126' extend radially inwardly toward toward the shaft sleeve to the ring's radially inner surface 130, 130' at a diameter preferably only slightly greater than the local outer diameter of the shaft sleeve thereat.

Flanges 128, 128' may be constructed in various manners. For example, in the embodiment of FIG. 5, flanges 128, 128' are formed by applying strip 132 to circumferential slot 134 on the outer surface 122 of ring 120 having flanges 128, 128' angled at 45° from surface 122. In the embodiment of FIG. 5A, the 45° flanges axe stamped out of sidewalls 126, 126°.
3Ring 120 further defines an interior circumferential surface 136 extending axially between the interiors of sidewalls 126, I26', thus forming the internal flow channel 121 wl2ich cooperates with the vane-bearing local sleeve surface thereat. The flow channel serves for efficient conveyance of barrier fluid from and to ports 110, 112 and throughout the barrier-fluid receiving areas 140 within the seal, i.e., between the sleeve outer surface and the inner surfaces of all of seal members 42, 54, 42', 54' up to O~-rings 34, 86.
sting 120 is further provided with radially inwardly deflected flanges 142, 144 extending through.
ring outer and inner surfaces 122 and 136, The inwardly deflected flanges define a dam 150 therebetween within flow channel 121. The dam obstructs fluid flow theneat, while fluid flown is unobstructed in the remaining portion of the flow channel. In the process of forming the flanges, a pair of radial passages 146, 148 are foamed radially penetrating the ring circumference adjacent to flanges 142, 144, respectively.

-2g_ The unobstructed portion of the flow channel provides a barrier-fluid flow path running between passages 146, 148, while the flanges direct fluid flow to and from passages 146, 148 into or out of the flow channel. Passages 146, 148 mate with the mouths of ports 110, 112 of the gland for transfer of barrier fluid therebetween, and form either an inlet or outlet depending on the direction of shaft rotation. In operation, at the inlet passage, the associated flange directs fluid flow inwardly between the rotating vane-bearing shaft sleeve and the unobstructed flow channel and at the outlet passage the associated flange directs the accelerated fluid outwardly out of the flow channel to the adjacent outlet port. As a result of this arrangement, the equipment shaft maybe rotated either clockwise or counter clockwise with optimized barrier fluid delivery in either case.
The gland of this embodiment is like that shown in FIG. 1 except that parts 110 , 112 are relocated corresponding to location of passages 146 and 146. For example, as shown in FIG. 5, passages 146 and 14B subtend an acute angle of about 40 degrees, enclosing dam 150 therebetween, and ports 110, 112 are located accordingly.
A portion of ring 120 at dam 150 defines a circumferential slot 154 opening radially ~utwardly from the ring circumference for receipt of lug 106 for rotationally locking the ring to the gland. This then non-rotatably locks primary sealing members 54, 54' to the gland via the ring, and also assures alignment of the inlet and outlet passages of the flow channel with respective mouths of the inlet and outlet ports of the seal.

FIG. 5B shows ring 120 of FIG. 5 in perspective view before attachment of the anti-rotation strips 132 in slots 134, and provides an additional view of slot 132 in slots 134, and provides an additional view of slot 154 (the latter for receiving anti-rotation lug 106) and passages 146, 148. FIG. 5C
is a top view of ring 120 of FIG. 5 with one of the strips 132 attached, and showing a practical view of stationaries 54, 54'. As shown, flanges 128, 128' of strip 132 cooperate with anti-rotation notches 64, 64' of stationaries 54, 54' to prevent rotation of the ring relative to the stationaries, and ant-rotation lug 106 (shown in dotted outline) mates in slot 154 to lock the ring to the gland (via lug crossbar 107) to prevent rotation of the ring relative to the gland. FIG. 6 shows an alternative embodiment of the assembly of FIG.

2 with ring 120 installed.
The respective seal ports couple with the respective ring passages to provide fluid delivery essentially tangetially to the shaft central axis, so as to minimize turbulence on fluid transfer at the flow channel. Preferably the cross-section of each of the port mouths (e. g., mouth 156 of port 110 shown in FIG.
6) is greater than the cross-section of the passage 146 or 148 associated therewith so that a fluid flow path can be maintained regardless of misalignment therebetween occasioned by axial shifting of the ring relative to the gland.
In operation, as the sleeve and vanes 65 on the sleeve shift axially, the seal members 42, 54, 42', 54' shift with ring 120 floating axially between seal members 54, 54'. This arrangement maintains the flow channel centered over the pumping vanes so as to optimize delivery of the cooling barrier fluid to the axially shifted seal surfaces regardless of shaft barrier fluid to the axially shifted seal surfaces regardless of shaft endplay. Ideally, the ring cooperates with the shaft sleeve and gland with such dimensions and tolerances to permit the ring to shift with the gland-mounted stationary seal members 54, 54' for accomodating both endplay and runout of the rotating shaft.
Other embodiments of this invention which will occur to those skilled in the art are within the scope of the following claims. For example, it would be possible to employ a single stationary seal having two seal facees in conjuction with a split gland.

Claims (53)

1. A double mechanical seal assembly having a gland for fixed attachment to a housing of equipment having a rotary shaft means, the shaft means comprising a shaft which is subject to endplay and fluid-flow acceleration vanes associated with said shaft, said gland having an interior surface for non-rotatably receiving a pair of annular primary seal members having seal faces which mate with a respective seal face of a second pair of annular primary seal members which are non-rotatably mounted to said shaft means, said primary seal members forming two pairs of mated seal faces defining a sealed barrier-fluid environment, a first pair of said mated seal faces sealing process fluid along said shaft means in a process-fluid environment, said gland having a pair of ports extending radially therethrough and each port having a mouth located for opening into said barrier-fluid environment adjacent to said vanes for providing barrier-fluid flow thereat in a direction of rotation of said shaft means when said gland is mounted to said equipment concentrically to said shaft, the seal comprising an axially floating, annular flow ring having an outer circumferential surface for mounting to said gland interior adjacent to said port mouths and axially between said primary seal members associated with said gland, an interior of said floating ring comprising an obstructed flow channel, said floating ring having sidewalls extending radially inwardly to an inner diameter of said floating ring, said flow channel defined along an inner circumferential surface of said floating ring axially located between said sidewalls, said floating ring further comprising a pair of passages extending radially through said outer and inner circumferential surfaces, said ring interior further including a dam located between said passages, said dam blocking fluid flow between said passages in a first rotational direction in said flow channel, said passages floatingly communicating with ones of said gland port mouths to facilitate flow of barrier fluid through said ports, passages, and flow channel, in a second rotational direction, mounting means for non-rotatably mounting said floating ring and said primary seal members associated with said gland to said gland, said mounting means permitting axial travel of said gland-mounted primary members and said floating ring to accommodate axial shifting of said shaft means while sealing barrier fluid flow in said barrier-fluid environment, whereby said axial travel of said floating ring maintains said flow channel located adjacent to said vanes regardless of shaft endplay while said mated seal faces remain mated, and biasing means for applying a biasing force against the primary seal members.

2. The seal assembly of claim 1 wherein each said sidewall comprises a lock structure, wherein each one of said first pair of primary seal members has an axial seal face at one end thereof and said means for non-rotatably mounting comprises the other end of each of said first pair of primary seal members, each said other end comprising at least one key structure, each said sidewall lock structure cooperating with said at least one key structure for non-rotatably locking said first pair of primary seal members to said flow ring.

3. The seal assembly of claim 2 wherein said sidewall lock structure comprises a flange and said at least one key structure comprises a notch.

4. The seal assembly of claim 1 wherein said means for non-rotatably mounting further comprises a recess defined in said gland and a recess defined in said outer circumferential surface of said floating ring and a lug for mating in said recesses and for locking said floating ring against rotation in said gland but facilitating axial shifting of said ring.

5. The seal assembly of claim 1 wherein said means for non-rotatably mounting comprises a resilient secondary seal for mounting one said primary seal member associated with said gland resiliently to said gland.

6. The seal assembly of claim 4 wherein said means for non-rotatably mounting includes a first O-ring mounted between, and separating from physical contact, said gland interior and a local sealing surface of one said primary seal members associated with said gland, and a second O-ring mounted between and separating from physical contact, said gland interior and a local sealing surface of the other of said primary seal members associated with said gland.

7. The seal assembly of claim 1 wherein said floating ring further comprises a pair of flanges deformed radially inwardly from said outer and inner circumferential surfaces and creating said pair of passages extending radially through said outer and inner circumferential surfaces.

8. The seal assembly of claim 7 wherein said flanges are deformed radially inwardly to said inner diameter of said floating ring.

9. The seal assembly of claim 1 wherein said equipment housing comprises a central annulus defining a stuffing box and through which said shaft means extends, wherein said shaft has a central axis and the housing has a central axis, said axes being aligned, wherein said central axes are subject to misalignment with each other, and wherein said means for non-rotatably mounting comprises means for isolating misalignment between the central axis of said shaft and the central axis of said stuffing box from said seal faces, for maintaining said seal faces essentially perpendicular to said shaft regardless of any such misalignment.

10. The seal assembly of claim 9 wherein said means for isolating comprises a sleeve assembly for mounting on said shaft, said assembly including a sleeve with a flange at one end and spring means on the other end thereof, for maintaining uniform spring load across all seal faces regardless of any said misalignment thereof, said vanes formed on an outer surface of said sleeve.

11. The seal assembly of claim 10 wherein one of said primary seal members is axially resiliently mounted on said sleeve, said primary seal members being mounted under uniform compression from said spring means and transmitting said compression from said spring means through said floating ring to said flange.

12. The seal assembly of claim 11 wherein said spring means comprises compression springs located circumferentially about one end of said sleeve assembly concentrically to said shaft, said means for isolating comprising isolating structure for preventing flexure of said springs regardless of any said misalignment.

13. The seal assembly of claim 12 wherein said springs are located outside of said equipment and of said gland and are isolated by one of said pairs of seal faces from said process-fluid and from said barrier-fluid environments.

14. The seal assembly of claim 13 wherein said primary seal members each define generally radially extending piston areas on non-seal-face rear sides thereof, the piston areas radially aligned with and smaller than a contact area of the seal faces, and each piston area being a predetermined fixed area equal to a major portion of the contact area.

15. The seal assembly of claim 14 wherein said means for non-rotatably mounting comprises a resilient secondary seal for mounting one said primary seal member associated with said gland resiliently to said gland, further comprising a resilient secondary seal for mounting one said primary seal member associated with said sleeve slidably to said sleeve, said resilient secondary seals being located on the rear sides of said primary seal members at fixed positions spaced axially from said seal faces to prevent passage of fluid axially along said primary seal members.

16. A flow ring for use in a mechanical seal assembly having a first primary seal member associated with a stationary structure of equipment to be sealed and a second primary seal member associated with a shaft of the equipment, and having a barrier fluid chamber defined between the first primary seal member and a second structure mounted concentrically to the shaft, the seal members defining relatively rotatable mating seal faces which define a contact area therebetween for sealing a process fluid within said equipment, the seal assembly including a gland for stationary mounting to said equipment concentrically to said shaft, said gland defining a central annulus for receipt of said shaft and further defining fluid ports opening out through an interior of said gland for flowing of barrier fluid in said seal assembly to cool said primary seal members, said gland interior receiving said first primary seal member for mounting in said seal assembly, said flow ring comprising an axially floating, annular ring having an outer circumferential surface for mounting to the interior of said gland adjacent to said ports and axially adjacent an end of said primary seal member associated with said gland, said ring having a lock means for being non-rotatably locked to said gland, said ring having an interior circumferential surface comprising an obstructed flow channel for flowing of barrier fluid in said seal assembly.

17. The ring of claim 16 further comprising a pair of passages extending radially through said outer and inner circumferential surfaces, said ring interior further including a dam located between said passages, said dam blocking fluid flow between said passages in a first rotational direction in said flow channel, said passages floatingly communicating with said gland ports to facilitate flow of barrier fluid through said ports, passages and flow channel in a second rotational direction.

18. The ring of claim 17 wherein said shaft comprises vanes associated therewith for acceleration of barrier fluid flowing through said ports by rotation of said shaft, said ring further comprising mounting means for non-rotatably mounting said floating ring and said primary seal member associated with said gland to said gland, said mounting means permitting axial travel of said gland-mounted primary member and said floating ring to accommodate axial shifting of said shaft, whereby said axial travel of said floating ring maintains said flow channel located adjacent to said vanes regardless of shaft endplay while said mated seal faces remain mated.

19. The ring of claim 18 wherein said floating ring has sidewalls extending radially inwardly to define an inner diameter of said floating ring, said flow channel defined along said inner circumferential surface of said floating ring axially located between said sidewalls.

20. The ring of claim 19 wherein each said sidewall comprises a lock structure, wherein said first primary seal member has an axial seal face at one end thereof and said means for non-rotatably mounting comprises the other end of said primary seal member, said other end comprising at least one key structure, one said sidewall lock structure cooperating with said at least one key structure for non-rotatably locking said primary seal member to said flow ring.

21. The ring of claim 20 wherein said sidewall lock structure comprises a flange and said at least one key structure comprises a notch.

22. The ring of claim 21 wherein said means for non-rotatably mounting further comprises a recess defined in said outer circumferential surface of said floating ring and a lug for mating in said recess and in said gland for locking said floating ring against rotation in said gland but facilitating axial shifting of said ring.

23. The ring of claim 1 or 17 wherein said pair of passages extend radially through said outer and inner circumferential surfaces to subtend an acute angle therebetween for cooperation with gland ports subtending a like angle.

24. The ring of claim 1 or 17 wherein said pair of passages extend radially through said outer and inner circumferential surfaces to subtend an angle of about 40 degrees therebetween for cooperation with gland ports subtending a like angle.

25. A method for improving a flow of barrier fluid within a mechanical seal assembly, the seal assembly of the type having the parts comprising a first primary seal member associated with a stationary structure of equipment to be sealed and a second primary seal member associated with a shaft of the equipment, and having a barrier fluid chamber defined between the first primary seal member and a second structure mounted concentrically to the shaft, the seal members defining relatively rotatable mating seal faces which define a contact area therebetween for sealing a process fluid within said equipment, the seal assembly including a gland for stationary mounting to said equipment concentrically to said shaft, said gland defining a central annulus for receipt of said shaft and further defining fluid ports opening out through an interior of said gland for flowing of barrier fluid in said seal assembly to cool said primary seal members, said gland interior receiving said first primary seal member for mounting in said seal assembly, said method comprising the steps of providing an axially floating, annular flow ring having an outer circumferential surface for mounting to the interior of said gland adjacent to said ports and axially adjacent an end of said primary seal member associated with said gland, providing said ring with a lock means for being non-rotatably mounted to said gland, and providing said ring with an interior circumferential obstructed flow channel for flowing of barrier fluid in said seal assembly.

26. A double balanced double mechanical seal assembly having a predetermined pressure balance for sealing process fluid in a first fluid environment at an inboard seal within a stuffing box of equipment concentric to a shaft of said equipment and having an outboard seal for sealing a second fluid environment between itself and said inboard seal, the seal assembly comprising relatively rotatable primary seal members defining said inboard and outboard seals and mounted substantially concentrically to said shaft, a plurality of secondary seals sealing said primary seal members with respect to said equipment within said seal assembly for sealing said first fluid environment from said second fluid environment, wherein each said primary seal member has a radial seal face side extending between an inner and outer diameter thereof defining a respective radially extending sealing face, said seal faces of a first pair of said primary seal members being mated to form said inboard seal over a first primary seal face contact area extending between first inner and outer primary seal face contact area diameters, said seal faces of a second pair of said primary seal members being mated to form said outboard seal over a second primary seal face contact area extending between second inner and outer primary seal face contact area diameters, bias means located only outside of said first fluid environment and applying a biasing force only against primary seal members forming said outboard one of said seals, thereby biasing all of said seal faces in one direction, each said primary seal member comprising, a side opposite said radial seal face side thereof, each said opposite side extending between an intermediate diameter thereof and one of said inner and outer diameters thereof, and comprising a fixedly predetermined generally radially extending piston area associated therewith, each said primary seal member piston area being defined as extending radially between said intermediate diameter of said primary seal member with which it is associated and one of said inner or outer primary seal face contact area diameters, and each said piston area being a predetermined fixed area equal to a major portion of said contact area, independent of thickness or location of said secondary seals.

27. The seal assembly of claim 26 wherein two of said primary seal member piston areas are exposed to said second fluid environment and another one of said primary seal member piston areas is exposed to said first fluid environment.

28. The seal assembly of claim 26 further comprising an isolation arrangement for isolating from said inboard and outboard seals misalignment between said shaft and said equipment, said primary seal members comprising rotary members associated with said shaft and stationary members non-rotatably associated with said equipment, said isolation arrangement including said biasing means for biasing said seal faces together, and a sleeve for mounting concentrically over said shaft, said sleeve having a flange extending radially essentially perpendicular to said shaft and said primary seal members mounted in said seal assembly relative to said flange with said seal faces held essentially perpendicular to said shaft regardless of any said misalignment, said rotary members of said primary seal members mounted by said secondary seals on said sleeve substantially concentrically to said shaft, and one of said rotary members and one of said stationary members of said primary seal members slidably mounted by said secondary seals concentrically to said shaft, respectively, said sleeve supporting said biasing means and said primary seal members such that bias from said biasing means biases said seal faces uniformly toward said flange, whereby said seal assembly maintains pressure balance across said seal faces regardless of said misalignment.

29. The seal assembly of claim 28 wherein said biasing means comprises compression springs mounted on said sleeve outside of said first or second environment for uniformly biasing said primary seal members up to said flange.

30. The seal assembly of claim 26 further comprising a sleeve for mounting concentrically over said shaft and a gland for mounting to said equipment, wherein two of said primary seal members are non-rotatably mounted to said gland with associated ones of said secondary seals associated with and sealing said two members thereto and wherein two of said primary seal members are rotatably mounted to said sleeve with respective associated said secondary seals associated with and sealing said two members thereto, said gland having at least one recess along its inside diameter for capture of at least one of said secondary seals and preventing their axial displacement within said seal assembly, and said sleeve defining a recess for capture of at least one of said secondary seals and preventing their axial displacement within said seal assembly.

31. A double balanced double mechanical seal assembly comprising a sleeve, first and second pairs of relatively rotatable primary seal members, each said pair having first and second radially extending opposed seal faces contacting each other over predetermined contact areas to form a seal, thereby, said sleeve having a flange at one end thereof with a surface extending radially outwardly essentially perpendicular to an inner surface of said sleeve;
said primary seal members being assemblable on said sleeve in serial abutting relation with each other and with a non-seal-face side of an inboard one of said primary seal members abutting said flange surface, said inboard one and said primary seal member furthest from said inboard one being connected to said sleeve for rotation therewith, the other said primary seal members being intermediate members for connection to a stationary structure;
and a biasing means being connected to said sleeve only at the non-flange end of said sleeve, said biasing means contacting said primary seal member furthest from said inboard member for biasing said primary seal members in one direction with respect to and toward said flange.

32. A mechanical seal assembly comprising a first primary seal member associated with a stationary structure of equipment to be sealed and a second primary seal member associated with a shaft of said equipment, said equipment having a central axis and being of the type having a stuffing box through which the shaft extends axially along said central axis, the seal members defining relatively rotatable seal faces which mate to define a radial contact area therebetween for sealing a process fluid within said equipment, the seal assembly comprising a gland comprising a stationary structure for stationary mounting to said equipment concentrically to said shaft, said gland defining a central annulus for receipt of said shaft, and isolation means for isolating misalignment between said shaft and said central axis from said seal faces such that said seal faces generally remain mating and remain perpendicular to said shaft, regardless of any said misalignment, said isolation means comprising a sleeve assembly for mounting on said shaft, said sleeve assembly including a sleeve with a flange at one end of said sleeve, wherein said first and second primary seal members form a first seal at their mating seal faces, and a third primary seal member mounted to said gland and a fourth primary seal member resiliently mounted to said sleeve form a second seal at their mating seal faces, said first primary seal member and said third primary seal member each being sealed by a respective secondary seal to said gland and said second primary seal member and said fourth primary seal member each being sealed by a respective secondary seal to said sleeve, said sleeve sealed by another secondary seal to said shaft, wherein said first primary seal member in cooperation with said second primary seal member and associated secondary seals seal process fluid from within said equipment from passage to said second seal, wherein said first and second seals form a chamber for receipt of a barrier fluid, said seal assembly also including biasing means mounted at the other end of said sleeve, said sleeve assembly and biasing means maintaining uniform biasing across all said seal faces regardless of any said misalignment, said biasing means including a plurality of springs and said secondary primary seal member being axially slidably mounted on said sleeve, said first and second primary seal members being mounted under uniform compression from said springs and transmitting said compression from said springs to said flange, and wherein said compression springs are located circumferentially about only one end of said sleeve assembly concentrically to said shaft, said isolation means preventing flexure of said springs regardless of any said misalignment.

33. The seal assembly of claim 32 wherein said springs are located outside of the equipment and of said gland and are isolated from said process or barrier fluid.

34. The seal assembly of claim 32 wherein said primary seal members each define a generally radially extending piston area on a rear side thereof, said piston areas axially aligned with said seal face contact area, and each piston area being a predetermined fixed area equal to a major portion of said contact area.

35. The seal assembly of claim 33 wherein said respective ones of said secondary seal fixed diameters of said primary seal members on said rear sides thereof at positions spaced axially from said seal faces, to prevent passage of fluid axially along said primary seal members.

36. The seal assembly of claim 34 wherein said gland comprises barrier fluid ports communicating with said barrier fluid chamber, and wherein said primary seal members have extensions with apertures extending radially therethrough for permitting barrier fluid access between said sleeve and surfaces of said primary seal members thereadjacent.

37. A mechanical seal assembly for retaining process fluid within equipment, the equipment having a relatively rotary part and a relatively stationary housing part, the interior of said housing part forming a stuffing box, each said part being concentric to a central axis of said equipment, said housing part for mounting of said seal assembly concentrically to said equipment central axis, said rotary part being axially shiftable under load between a first and second axial position relative to said housing part, said seal assembly having a first and a second pair of primary seal members, each said pair having a rotary primary real member associated with said rotary part and a stationary primary seal member associated with said stationary part, said members of each said pair having surfaces defining relatively rotatable seal faces which mate to define an associated seal face contact area, raid associated contact area of said first pair defining an axially inboard seal proximally associated with said stuffing box and which is fluidly loaded thereat and said contact area of said second pair forming an outboard seal which is fluidly loaded thereat and which is outboard from said inboard seal, said seal assembly having a central axis and said inboard and outboard seal being formed concentric to said seal assembly axis, said seal assembly further comprising biasing means for applying axial bias to said seal faces, and a support sleeve for mounting concentrically over said rotary part, said support sleeve having an inboard support structure extending radially and essentially perpendicular to said rotary part, said primary seal members being mounted relative to said support sleeve such that said seal faces are held essentially perpendicular to said rotary part, with one of said rotary primary seal member and both of said stationary primary seal members being axially slidably mounted relative to said support sleeve for sliding toward said support structure according to bias from said biasing means, and said support sleeve supporting said biasing means and said slidable ones of said primary seal members such that said bias from said biasing means and net fluid load from said loaded inboard and outboard seals is persistently and evenly applied to said inboard and outboard seals, transmitted through said primary seal members between said biasing means and said support structure, regardless of shifting of said rotary part between said first and second axial positions.

38. The seal assembly of claim 37 wherein said inboard and outboard seals define axially inboard and outboard sides of a fluid flow section of said seal assembly for flow of a barrier fluid within said seal assembly, wherein said equipment rotary part includes a shaft and said support sleeve is configured for mounting on said shaft, said sleeve having an outer mounting surface for mounting of said rotary primary seal members, said support structure comprising a flange of said sleeve extending perpendicularly radially from said sleeve mounting surface, said biasing means being associated with an end of said sleeve with said primary seal members mounted concentrically to said sleeve and biased by said biasing means toward said flange, said rotary primary seal members being coupled to said sleeve via a respective secondary seal with the side opposite to the seal face side of each of said rotary primary seal members being substantially exposed to a common fluid environment, said inboard seal for sealing a first fluid pressure differential and said outboard seal for sealing a second fluid pressure differential, the combination of net sealed pressure plus the bias from said biasing means applying a net axial forage to said flange via said primary seal members.

39. The seal assembly of claim 37 wherein said biasing means comprises compression springs located circumferentially about an outboard end of said sleeve assembly, said support sleeve isolating from said inboard and outboard seals the effect of axial shifting of said shaft between said first and second axial positions and substantially preventing flexure of said springs regardless of any said axial shifting.

40. The seal assembly of claim 38 wherein said seal assembly further includes a gland for mounting of said seal to said housing part, said stationary primary seal members each sealed by a respective secondary seal to said gland, said sleeve sealed by an inner secondary seal to said shaft, and wherein said fluid flow section comprises a chamber within said seal assembly, wherein said gland comprises barrier fluid ports communicating with said chamber, and wherein said stationary primary seal members have extensions with apertures extending radially therethrough for permitting barrier fluid access between said sleeve and surfaces of said seal members thereadjacent in said chamber.

41. The seal assembly of claim 40 wherein paid biasing means comprises compression springs located outside of the equipment and said gland, said springs isolated by said outboard seal and associated secondary seals from said process or barrier fluids.

42. The seal assembly of claim 37 wherein said primary seal members each define a generally radially extending piston area on a non-seal-face side thereof, each said piston area radially aligned with and smaller than said contact area associated therewith, and each said piston area being a predetermined fixed area equal to a major section of said associated contact area.

43. The seal assembly of claim 42, wherein each said primary seal member defines a generally radially extending piston area on a non-seal-face side thereof, said piston areas radially aligned with and smaller than its associated said contact area, and each piston area being a predetermined fixed area equal to a major section of its associated said contact area, wherein a plurality of secondary seals seal fixed diameters of raid primary seal members at positions spaced axially from said seal faces thereof to prevent passage of fluid axially along said seal members.

44. The seal assembly of claim 37 wherein an outermost one of said primary seal members of said second primary seal member pair is positioned at said outboard end of said seal assembly with a non-seal-face side of said outermost member facing axially outwardly away from the others of said primary seal members, said outermost member outwardly facing aide comprising a generally radially extending outer piston area radially aligned with and smaller than said contact area associated with said second pair and having a predetermined fixed area equal to a major portion of said associated contact area, said outer piston area extending radially inwardly toward said support sleeve in fluid communication with an inner periphery of said primary seal members.

45. The seal assembly of claim 44 wherein an innermost one of said primary seal members of said first primary seal member pair is positioned at the inboard end of said seal assembly distal to said outermost primary seal member, with a non-seal-face side of said innermost one facing axially inwardly away from the others of said primary seal members, said piston area thereof extending radially inwardly and communicating with the inner periphery of said primary seal members, said piston areas of said innermost and outermost primary seal members being equal.

46. The seal assembly of claim 44 wherein a non-seal-face side of an innermost primary seal member abuts a flange, and wherein an innermost one of said primary seal members of said first primary seal member pair is positioned at the inboard end of said seal assembly distal to said outermost primary seal member, with the non-seal-face side of said innermost one facing axially inwardly away from the others of said primary seal members, said piston area thereof extending radially inwardly and communicating with the inner periphery of said primary seal member, and wherein said biasing means comprises compression springs at an outer end of said sleeve, said springs biasing all said primary seal members toward said flange.

47. The seal assembly of claim 46 wherein said innermost and outermost primary seal members each comprise an annular extension on a non-seal-face side thereof, said extensions having enlarge d inner diameters relative to inner diameters of the contact areas of said mated seal faces associated with said innermost and outermost primary seal members, the inner diameters of said extensions being equal to outer diameters of said piston areas of said innermost and outermost primary seal members, wherein a respective secondary seal seals positions axially spaced from said associated piston areas.

48. The seal assembly of claim 47 wherein said innermost and outermost primary seal members are mounted on said sleeve and the others of said primary seal members of said first and second primary seal member pairs each comprise an associated annular extension on said non-face-seal side thereof, raid associated extensions having reduced outer diameters relative to outer diameters of the contact areas of said seal faces associated with said others of said primary seal members, the outer diameters of the associated extensions being equal to inner diameters of said piston areas of said others of said primary seal members, further comprising a respective secondary seal for sealing against an associated one of said annular extensions of said others of said primary seal members at position's spaced from the piston areas associated with said other of said primary seal members.

49. The seal assembly of claim 37 further comprising a secondary seal for sealing each said stationary primary seal member to said stationary housing part and a secondary seal for sealing each said rotary primary seal member to said support sleeve, wherein said primary seal members each define a generally radially extending piston area on a non-seal-face side thereof, each said piston area being radially aligned with and smaller than said contact area with which it is associated, and each said piston area being a predetermined fixed area equal to a major portion of said associated contact area, one of said secondary seals having a radial cross-section extending to a first inner diameter, and said contact area associated with said one of said secondary seals having a radial cross-section extending to an inner diameter which is independent of said first inner diameter.

50. The seal assembly of claim 49, wherein one primary seal member of said first pair of said primary seal members and one primary seal member of said second pair of said primary seal members each comprises an annular extension thereof on a side opposite its said seal face side, each said extension having a reduced outer diameter relative to an outer diameter of said contact area of the associated seal, each said reduced outer diameter of said extension defining an inner diameter of said piston area of the associated seal, one said secondary seal sealing against one said annular extension and another said secondary seal sealing against another said extension at positions spaced from each other and spaced from the associated said piston area.

51. The seal assembly of claim 50, wherein said seal assembly seals process fluid in said equipment in a first fluid environment at a seal associated with an innermost primary seal member and seals a second fluid environment between said seal associated with said innermost primary seal member and said seal associated with an outermost primary seal member, wherein two of said primary seal member piston areas are exposed to said second fluid environment and another one of said primary seal member piston areas is exposed to said first fluid environment.

52. The seal assembly of. claim 51, further comprising a sleeve for mounting concentrically over said shaft and an annular gland for mounting to said equipment concentrically to said shaft, wherein twa of said primary seal members are non-rotatably mounted to said gland with secondary seals associated with and sealing said two members to said gland and wherein two other of said primary seal members are rotatably mounted to said sleeve with secondary seals associated with and sealing said two other members to said sleeve, said gland having an inner diameter which defines a recess for capture of a respective one of said gland-associated secondary seals for preventing axial displacement of said gland-associated secondary seals within said seal assembly, and said sleeve defining a capture recess for capture of one of said sleeve-associated secondary seals for preventing axial displacement of said sleeve-associated secondary seals within said seal assembly.

53. A mechanical seal assembly for sealing a shaft of rotary equipment, the assembly having first and second pairs of primary seal members, each said pair of seal members including a stator seal member and a rotor seal member, each said seal member having a seal face side and a non-seal face side, and each said pair respectively defining a seal contact area where said respective stator and rotor seal member seal faces meet for forming a fluid seal thereat, a first of said pairs establishing an inboard seal adjacent to the equipment for sealing a first fluid environment and a second of said pairs establishing an outboard seal distal to said inboard seal for sealing a second fluid environment, the assembly comprising:
a sleeve with a bore for mounting of said sleeve on the equipment shaft, said sleeve having an axially extending outer surface for mounting of said rotor seal members thereon, said sleeve further comprising an inboard flange end and an outboard biasing end, said flange end having a flange surface radially extending essentially perpendicular to said sleeve outer surface, wherein said seal members are mounted concentrically to said shaft with one said rotor seal member being located furthest inboardly along said shaft adjacent to said equipment and the other said rotor seal member being located furthest outboardly along said shaft, said furthest inboard rotor seal member being mounted with its non-seal-face side abutting said flange surface, said furthest outboard rotor seal members having its non-seal-face side facing outboardly; and biasing means mounted on said sleeve at said sleeve outboard end and contacting said. non-seal-face side of said outboard rotor seal member for biasing all said seal members toward said flange.