WO1999049244A1 - Joint d'etancheite double pour gaz a surfaces d'etancheite coplanaires - Google Patents

Joint d'etancheite double pour gaz a surfaces d'etancheite coplanaires Download PDF

Info

Publication number
WO1999049244A1
WO1999049244A1 PCT/US1999/005319 US9905319W WO9949244A1 WO 1999049244 A1 WO1999049244 A1 WO 1999049244A1 US 9905319 W US9905319 W US 9905319W WO 9949244 A1 WO9949244 A1 WO 9949244A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotary
ring
stationary
radially
sealing
Prior art date
Application number
PCT/US1999/005319
Other languages
English (en)
Inventor
Alan O. Lebeck
Original Assignee
Utex Industries, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Utex Industries, Inc. filed Critical Utex Industries, Inc.
Priority to AU30799/99A priority Critical patent/AU3079999A/en
Priority to MXPA00009286A priority patent/MXPA00009286A/es
Priority to CA002325475A priority patent/CA2325475A1/fr
Priority to EP99912422A priority patent/EP1071895A1/fr
Publication of WO1999049244A1 publication Critical patent/WO1999049244A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
    • F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
    • F16J15/3412—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3464—Mounting of the seal
    • F16J15/348—Pre-assembled seals, e.g. cartridge seals

Definitions

  • the present invention relates to gas-lubricated non-contacting seals and, more particularly, to a gas lubricated seal with radial coplanar pad faces.
  • seal of the present invention has various applications, and is particularly well suited for sealing between a rotating drive shaft sleeve and a pump housing, so
  • lubricated seal may be selected for its inert qualities in view of the application, and
  • One type of gas seal uses circumferentially spaced grooves in one of the sealing faces.
  • the spiral grooves each extend radially inward from an outer - 2 - periphery of the respective sealing face. Pressurized gas is supplied to these
  • One such gas lubricated seal which is embodied in a cartridge design is the Type 2800 seal manufactured by
  • pressurized gas being supplied through the stationary ring and to circumferentially
  • coplanar double gas seals do not provide effective lift off of both the radially outer sealing face and the radially inner sealing face under various conditions. Also,
  • a double gas pressure seal is provided for sealing between a stationary housing and a rotary housing within the stationary housing.
  • the gas pressure seal includes a stationary ring and a rotary ring which cooperate to seal fluid within the stationary housing.
  • the stationary ring and a rotary ring which cooperate to seal fluid within the stationary housing.
  • housing may be a pump housing and the rotary housing may be a sleeve which is
  • the double gas seal is supplied with pressurized gas from an external source and at a pressure higher than the pressure of the
  • Each of the stationary ring and the rotary ring has an annular inner sealing
  • sealing engagement as used herein with respect to the sealing faces does not mean that the pad sealing faces are touching
  • a spring or other biasing member axially biases
  • annular groove is provided in one of the stationary ring and the rotary ring, with the annular
  • a plurality of circumferentially spaced inner recesses and a plurality of circumferentially spaced outer recesses are each provided in one of the stationary . 4 . ring and in the rotary ring, and preferably in the rotary ring.
  • Each inner recess is spaced between the annular groove and a radially innermost portion of the inner
  • each outer recess is spaced between the annular groove and a radially outermost portion of the outer sealing face is in
  • recesses exert a gas lift-off force on the axial movable one of the stationary ring and the rotary ring while providing a stiff pressurized gas film between the sealing
  • Each of the plurality of inner recesses and each of the plurality of outer recesses has a rotary leading portion and a circumferentially spaced rotary trailing
  • each of the sealing faces lies within a single
  • a supply port in one of the stationary ring and rotary ring supplies pressurized gas
  • annular groove through a plurality of inner feed channels to a plurality of inner
  • circumferentially spaced inner and outer recesses provide the desired pressurized - 5 - gas lift-off force which separates the stationary ring from the rotary ring while allowing a relatively small quantity of pressurized gas to leak from the gas
  • the double gas pressure seal may occupy
  • the gas pressure seal may be used over a wide range of external gas pressures and a wide range of fluid pressures within the stationary housing.
  • seal may be reliably used at elevated temperatures, and may be used to seal various types of fluids in the stationary housing, including abrasive, sticky, and corrosive
  • the gas pressure seal also has the ability to relatively contain fluids within
  • Figure 1 is a cross-sectional isometric view of a portion of a pump housing
  • FIG. 1 is an enlarged cross-sectional isometric view of a portion of the seal housing as shown in Figure 1, and illustrating one embodiment of a double
  • Figure 3 is a cross-sectional isometric view of the stationary ring shown
  • Figure 4 is a cross-sectional isometric view of the rotary ring shown in
  • Figure 5 is an end view of the rotary ring shown in Figure 2, illustrating the
  • Figure 6 is an end view of an alternate embodiment of a rotary ring according to the present invention.
  • Figure 1 illustrates one embodiment of the double gas pressure seal
  • a stationary seal housing 12 includes an
  • the pump includes a shaft 18 which rotates about axis 20 and extends through the housing 8 of the pump,
  • Gasket 22 which is secured to the inner housing 16, - 7 - thus seals against the face 7 of the pump housing 8. Process fluid in the pump thus occupies the annular gap 24 (see Fig. 2) between an outer portion of the gas
  • seal assembly 10 and both the inner housing 16 and the outer housing 14.
  • the rotary housing is a shaft sleeve 26, which rotates with the shaft 18.
  • a conventional pump drive collar 28 includes circumferentially spaced ports 30 each for receiving a respective set screw (not
  • a retaining ring 36 limits axial
  • circumferentially spaced centering disks 32 each secured to the outer housing 14 by a respective bolt 34 may be adjusted to properly center the axis 20 of the shaft
  • a static seal such as o-ring 38, may provide
  • seal assembly as described subsequently for sealing between these components during normal operation of the equipment. While the seal assembly
  • the double gas seal of the present invention may be used in various applications for sealing between a stationary component and a rotary
  • Exemplary equipment which may benefit from the seal assembly of this invention includes pumps and blower fans used in various operations,
  • the double gas seal of the present invention may be reliably used to
  • the gas pressure seal 10 includes a
  • the rotary ring 40 rotates with the sleeve
  • the item 9 is thus important to prevent overload between the stationary ring 42 and the rotary ring 40, thereby
  • the stationary ring 42 is similarly rotatably secured by pins (not shown) extending through drive ring 58
  • a static seal such as o-ring seal 44, seals between the rotary ring 40 and the sleeve 26.
  • a coil spring or other suitable biasing member 56 is provided in the outer
  • the drive ring 58 in turn acts on the - 9 - stationary ring 42, which then presses the end surface 60 of the rotary ring 40 into
  • the stationary ring 42 includes an annular groove 68 which is discussed in further detail
  • Each of these sealing faces lies within a plane perpendicular to the axis 20, and preferably both the radially inner and radially outer portions of both faces
  • 64 and 66 lie within a single plane perpendicular to the axis 20.
  • pressurized gas and preferably an inert
  • gas such as nitrogen
  • an external source such as supply
  • the pressurized gas is supplied to the input port 72 in the outer housing 14 and is transmitted through drilled passageway 74 to the annular cavity
  • cup shaped seals 46 and 48 also energizes the cup shaped seals 46 and 48 to provide a reliable seal between the stationary ring 42 and the outer housing 14.
  • the rotary ring 40 may be manufactured from the relatively hard material, such as silicon carbide, while the stationary ring 42 may be manufactured from a
  • the axial length of the portion 86 is from 0.100 inches
  • portion 86 is preferably from 100% to 115% of the radial thickness of the sealing
  • the portion 88 preferably has a radial thickness of about 70% to
  • the annular cavity 78 extends into the
  • each of the legs 80 and 82 is further restricted to form the relatively thin annular extensions 90 and 92 which are configured to receive the seals 46 and 48.
  • groove 78 may be controlled to provide a desired radial deflection capability for the legs 80 and 82 so that these legs may deflect in response to a radial pressure differential and thereby maintain a desired angular alignment between the
  • the annular groove 78 extends axially into the portion 88, and preferably extends into at least 20%, and
  • the recesses or pad faces themselves preferably should stay
  • the tabs 93 are provided to fix the rotational position of the ring 42 in place.
  • FIGS 4 and 5 illustrate the plurality of circumferentially spaced inner
  • each inner recess 94 includes a rotary leading portion 102 and a rotary trailing portion 104, and each
  • outer recess 96 similarly includes a rotary leading portion 106 and a rotary trailing
  • a plurality of circumferentially spaced holes 110 as - 12 - shown in Figure 4 may be provided in the rotary ring 40, with each hole 110 being sized to receive a suitable pin or other securing member to rotatably lock the
  • the pressurized gas which is sometimes referred to as a buffer
  • This gas is supplied between the two sealing faces 64 and 66. This gas may thus be
  • each ring has both a radially inward and a radially outward
  • This configuration desirably - 13 - provides a reduced space for the coplanar gas seal, and the parts of the seal are
  • the inner seal being an outside pressurized seal and the outer seal being an inside pressurized seal.
  • the recesses or pad faces are configured to cause the external
  • the desired gas seal thus includes a gas film with a thickness between these faces so that, as the faces move closer
  • radial thickness between the annular groove and the radially innermost edge of the inner recess 94 will be about 80% of the radial thickness between the annular
  • radial thickness between the annular groove and the radially outermost edge of the outer recess 96 will be about 80% of the radial thickness between the annular
  • a u-cup seal 46 intentionally will leak so that the process pressure - 14 - increases the sealing effectiveness of the seal 48. At this time, the seal 46 effectively is performing no sealing function, but the desired scaling function is still maintained by the seal 48.
  • the inner and outer recesses 94 and 96 may either use step pads or tapered pads.
  • the connecting channels 98 and 100 may each
  • Each of the inner and outer recesses 94 and 96 have a uniform depth of approximately 40% to 60% of the channel depth, i.e., typically from
  • the radially extending channels 98 and 100 may each
  • each recess has a depth of approximately 400 microinches
  • each outer recess may have a radial width 140 of approximately 50% of the spacing between the annular groove 68 and the outermost portion 144 of
  • the feed groove 100 may occupy approximately 15% of the tangential space between recesses, and the recess 96 itself may use approximately
  • tangential length 146 of the recess 96 is thus approximately 60% of the tangential length 148. Accordingly, the spacing 150 between the end of one recess 96 and - 15 - the beginning of the next feed groove may be approximately 25% of the tangential spacing 148.
  • the inner pad 94 is similarly proportioned. The inner pad radial
  • width 152 is thus approximately 50% of the spacing between the annular groove 68 and the innermost portion 155 of the sealing face 64.
  • recesses 94 and the plurality of outer recesses 96 define an area which is a
  • Figure 5 illustrates an outer sealing face area 154 radially outward of the groove 68 and an inner sealing face area 156 radially inward of the
  • the area of pad or recess 96 is at least 25% of the area 154, and preferably is at least 30% of the area 154.
  • area of pad or recess 94 is similarly at least 25% and preferably at least 30% of the area 156.
  • FIG. 6 illustrates another embodiment of the invention, wherein the
  • rotary pad 120 includes a plurality of circumferentially spaced inner recesses 122
  • Inner feed channels 126 extend between the annular groove and each respective inner recess, while
  • both the inner recesses and outer recesses are configured with respect to the feed
  • each recess is obviously the first portion of the recess which
  • a rotary leading portion 102 of a recess 94 first passes by the line 158, followed by the portion 104 of that same recess 94.
  • the plurality of inner and outer recesses could be provided on the stationary component rather than the rotary component, and in that case the
  • leading portion of each recess is the portion of the recess which first becomes
  • the carbon ring has a reduced axial length from the previously described embodiment, thereby making the carbon
  • An elongated rubber sleeve may then be provided
  • the rubber sleeve may be
  • an additional o-ring may be provided on the stationary ring and upstream from the cup shaped seals.
  • the biasing spring 56 may be eliminated, and the
  • biasing force desired to press the axially movable one of the rings against the other ring may be provided by the external pressurized gas.
  • the feed channels that supply the pressurized gas to the recesses and the
  • both the feed channels and the recesses may be provided on either the stationary ring or the rotary ring.
  • both the feed channels and the recesses are provided on the rotary ring.
  • Both the feed channels and the recesses are also preferably provided in the ring which is formed from the hardest material for the rotary ring and the
  • the annular groove 68 may be provided on either the stationary ring or the

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Sealing (AREA)

Abstract

L'invention concerne un joint d'étanchéité (10) double pour gaz sous pression, permettant d'assurer l'étanchéité entre un logement fixe (14) et un logement rotatif (26). Le joint d'étanchéité pour gaz comprend une bague fixe (42) et une bague rotative (40), chacune possédant une face d'étanchéité radiale interne et une face d'étanchéité radiale externe. Un ressort de sollicitation (56) pousse l'une des bagues vers l'autre. Une rainure annulaire (68) est située sur l'une des bagues, la rainure étant disposée espacée entre les faces d'étanchéité radiales internes et les faces d'étanchéité radiales externes. Un orifice d'alimentation (84) fournit du gaz sous pression à la rainure annulaire, à une pression supérieure à celle du fluide de traitement dans le logement fixe. Une pluralité d'évidements (94, 96) radialement internes et externes sont fournis sur l'une des bagues, et des canaux d'alimentation (98, 100) correspondants relient fluidiquement la rainure annulaire et une partie avant rotative de chaque évidement respectif. Une petite quantité de gaz sous pression s'échappe entre les faces d'étanchéité internes, dans l'atmosphère, et entre les faces d'étanchéité externes, vers le fluide de traitement enfermé de manière étanche dans le logement fixe.
PCT/US1999/005319 1998-03-23 1999-03-10 Joint d'etancheite double pour gaz a surfaces d'etancheite coplanaires WO1999049244A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
AU30799/99A AU3079999A (en) 1998-03-23 1999-03-10 Double gas seal with coplanar pad faces
MXPA00009286A MXPA00009286A (es) 1998-03-23 1999-03-10 Sello de gas doble con caras de cojin coplanares.
CA002325475A CA2325475A1 (fr) 1998-03-23 1999-03-10 Joint d'etancheite double pour gaz a surfaces d'etancheite coplanaires
EP99912422A EP1071895A1 (fr) 1998-03-23 1999-03-10 Joint d'etancheite double pour gaz a surfaces d'etancheite coplanaires

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US7904598P 1998-03-23 1998-03-23
US60/079,045 1998-03-23

Publications (1)

Publication Number Publication Date
WO1999049244A1 true WO1999049244A1 (fr) 1999-09-30

Family

ID=22148075

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1999/005319 WO1999049244A1 (fr) 1998-03-23 1999-03-10 Joint d'etancheite double pour gaz a surfaces d'etancheite coplanaires

Country Status (5)

Country Link
EP (1) EP1071895A1 (fr)
AU (1) AU3079999A (fr)
CA (1) CA2325475A1 (fr)
MX (1) MXPA00009286A (fr)
WO (1) WO1999049244A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9353865B2 (en) * 2014-06-03 2016-05-31 Thermo King Corporation Mechanical face seal

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1876515A (en) * 1932-09-06 Shaft packing
US2247505A (en) * 1939-01-13 1941-07-01 Joseph H Kohler Seal
US2265953A (en) * 1939-12-28 1941-12-09 Allis Chalmers Mfg Co Rotary shaft seal
US3572727A (en) * 1969-07-16 1971-03-30 Sealol Unloading gas barrier face seal
US3675935A (en) * 1970-07-13 1972-07-11 Nasa Spiral groove seal
US3744805A (en) * 1968-06-08 1973-07-10 Kupfer Asbest Co Slide ring for axially acting shaft sealing rings
US4461487A (en) * 1982-04-01 1984-07-24 Eagle Industry Co., Ltd. Stern tube seal
US4523764A (en) * 1982-06-25 1985-06-18 M.A.N. Maschinenfabrik Augsburg-Nurnberg Aktiengesellschaft Fluid-sealed shaft seal with bores for supplying and discharging fluid
US5066026A (en) * 1990-06-11 1991-11-19 Kaydon Corporation Gas face seal
US5071141A (en) * 1990-07-17 1991-12-10 John Crane Inc. Spiral groove seal arrangement for high vapor-pressure liquids

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1876515A (en) * 1932-09-06 Shaft packing
US2247505A (en) * 1939-01-13 1941-07-01 Joseph H Kohler Seal
US2265953A (en) * 1939-12-28 1941-12-09 Allis Chalmers Mfg Co Rotary shaft seal
US3744805A (en) * 1968-06-08 1973-07-10 Kupfer Asbest Co Slide ring for axially acting shaft sealing rings
US3572727A (en) * 1969-07-16 1971-03-30 Sealol Unloading gas barrier face seal
US3675935A (en) * 1970-07-13 1972-07-11 Nasa Spiral groove seal
US4461487A (en) * 1982-04-01 1984-07-24 Eagle Industry Co., Ltd. Stern tube seal
US4523764A (en) * 1982-06-25 1985-06-18 M.A.N. Maschinenfabrik Augsburg-Nurnberg Aktiengesellschaft Fluid-sealed shaft seal with bores for supplying and discharging fluid
US5066026A (en) * 1990-06-11 1991-11-19 Kaydon Corporation Gas face seal
US5071141A (en) * 1990-07-17 1991-12-10 John Crane Inc. Spiral groove seal arrangement for high vapor-pressure liquids

Also Published As

Publication number Publication date
EP1071895A1 (fr) 2001-01-31
CA2325475A1 (fr) 1999-09-30
AU3079999A (en) 1999-10-18
MXPA00009286A (es) 2002-05-08

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