US3589738A - Mechanical seal for pulp pumps - Google Patents

Mechanical seal for pulp pumps Download PDF

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Publication number
US3589738A
US3589738A US832967A US3589738DA US3589738A US 3589738 A US3589738 A US 3589738A US 832967 A US832967 A US 832967A US 3589738D A US3589738D A US 3589738DA US 3589738 A US3589738 A US 3589738A
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US
United States
Prior art keywords
seal ring
shaft
seal
stuffing box
rotary
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
US832967A
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English (en)
Inventor
Herbert E Tracy
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BW IP International Inc
Original Assignee
Borg Warner Corp
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Filing date
Publication date
Application filed by Borg Warner Corp filed Critical Borg Warner Corp
Application granted granted Critical
Publication of US3589738A publication Critical patent/US3589738A/en
Assigned to BORG-WARNER INDUSTRIAL PRODUCTS, INC. reassignment BORG-WARNER INDUSTRIAL PRODUCTS, INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: BORG-WARNER CORPORATION
Assigned to CITIBANK, N.A. reassignment CITIBANK, N.A. SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BORG-WARNER INDUSTRIAL PRODUCTS, INC.,
Assigned to BW/IP INTERNATIONAL, INC., ("BW/IP"),A CORP. OF DE. reassignment BW/IP INTERNATIONAL, INC., ("BW/IP"),A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: BORG-WARNER CORPORATION, A DE. CORP.
Anticipated expiration legal-status Critical
Assigned to CITIBANK, N.A. reassignment CITIBANK, N.A. RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: BW/IP INTERNATIONAL INC. (FORMERLY KNOWN AS BORG-WARNER INDUSTRIAL PRODUCTS, INC.)
Expired - Lifetime legal-status Critical Current

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    • 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
    • F16J15/342—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 with means for feeding fluid directly to the face

Definitions

  • ABSTRACT A mechanical seal assembly for paper pulp [51] Int. Cl .1 Fl6j /34, pumps in which clean fluid flows between the seal faces and Fl6j 15/54 flushes the pulp from the seal assembly.
  • the present invention provides a mechanical seal for use in the stuffing box of a pump for paper pulp, wherein the mechanical seal is particularly adapted for such service.
  • the present mechanical seal includes a structure which enables flushing of the pulp from the seal assembly with a small volume of flushing fluid, such as water.
  • the invention contemplates a mechanical seal assembly in which a rotary seal ring assembly is carried by the pump shaft, a stationary seal ring is carried by a fixed portion of the seal assembly, and passageways are provided for conducting a flushing fluid, such as water, between the seal faces at a pressure in excess of the internal stuffing box pressure. More particularly, the flushing fluid passageways are in the nonrotatable seal ring, and in accordance with one embodiment of the invention, a-further passage or path is provided for the flow of flushing fluid past the outer periphery of the seal rings which is exposed to the pulp.
  • a flushing fluid such as water
  • An object of the invention is to provide a mechanical seal assembly for use in the stuffing box of a pump which is used to pump a liquid containing solids, such as paper pulp, the assembly being easy to manufacture and install and requiring the use of substantially less flushing water than has been heretofore the practice with conventional packings.
  • FIG. 1 is a view in longitudinal section of a pump stuffing box and a mechanical seal made in accordance with the invention
  • FIG. 2 is a vertical section, as taken on the line 2-2 of FIG.
  • FIG. 3 is an enlarged fragmentary section, as taken on the line 3-3 of FIG. 2, showing the details of the mechanical seal elements;
  • FIG. 4 is a view corresponding to FIG. 3, but showing a modified embodiment of the invention.
  • FIGS. 1 through 3 an embodiment of the present mechanical seal is illustrated as being applied to a pump housing 1 having a stuffing box 2.
  • a pump shaft 3 Rotatable in the stuffing box 2 is a pump shaft 3 on the inner end 4 of which is disposed the hub 5 of the usual pump impeller (not shown).
  • the seal assembly comprises a shaft sleeve 6 of cylindrical form disposed about the shaft 3.
  • a key 7 is disposed in a key slot 8 in the shaft 3 and in a keyway 9 in the inner periphery of the shaft sleeve 6, whereby the shaft 3 and sleeve 6 are rotatable as a unit.
  • An end flange 10 of the sleeve 6 is held against a shaft shoulder 11 by the impeller hub 5, and a suitable sealing gasket 12 is interposed between the flange 10 and the shoulder 11 to preclude leakage from the pump housing between the sleeve 6 and the shaft 3.
  • a stationary seal ring 13 and a rotatable seal ring 14 which are respectively provided with radial seal faces 15 and 16 disposed in confronting relation and preferably lapped to an optical flat, as is customary in the case of mechanical seals.
  • the stationary seal ring 13 is carried by the usual seal flange 17- which is secured to the pump housing 1 as by a suitable number of screw fasteners 18.
  • An appropriate sealing gasket 19 is interposed between the seal flange 17 and the pump housing 1 to prevent leakage therebetween.
  • the seal flange 17 is provided with a bore 20 in which the seal ring 13 is disposed, axial movement of the seal ring 13 being precluded by a marginal lip 21 of the seal flange 17 which defines an opening 22 through which the shaft sleeve 6 extends.
  • a flushing fluid is employed to flush pulp or other solid material entrained in fluid in the pump housing 1 from the region of the opposing seal faces 15 and 16 and from the stuffing box 2.
  • the seal flange 17 includes a flushing fluid inlet passage 23 which leads to an annular passageway 24 formed within the bore 20 of the flange 17.
  • the seal ring 13 has a number of radial passages 25 which communicate with annular passage 24, and, in addition, the ring 13 has a number of circumferentially spaced passages 26 which connect the passages 25 with a like number of circumferentially spaced arcuate fluid passages 27 forming flushing fluid chambers between the seal faces 15 and 16.
  • the chambers or passages 27 are formed in the seal face 15 of the seal ring 13, but it will be understood that such chambers may, if desired, be formed in the seal face 16 of the rotary seal ring 14.
  • flushing fluid is confined to the path defined by the inlet passage 23, the annular passage 24, the radial passages 25, and the connecting;
  • the stationary seal ring 13 is provided with a pair of axially spaced, circumferentially extended, resilient seal rings 28 and 29 which sealingly engage within the bore 20 at opposite sides of the annular passage 24.
  • the rotary seal ring 14 is driven by a spring carrier 30 which includes an annular body section 31.
  • This body section 31 of the spring carrier 30 is clamped to the shaft sleeve 6 by one or more setscrews 32 which are threadedly engaged in the body 31 at one side of a diametrical line extended across the spring carrier 30.
  • a pair of the setscrews 32 is spaced 90 apart, and, when threaded inwardly into engagement with the shaft sleeve 6, the setscrews 32 cause a clamping of the opposite side of the spring carrier 30 against the shaft sleeve 6, causing, for a purpose which will hereinafter be described, a gap 33 between the spring carrier 30 and the shaft sleeve 6.
  • the rotary seal ring 14 is disposed within an axially extended skirt portion 34 of the spring carrier 30, the skirt portion 34 having a cylindrical bore 35 in which the outer periphery of the seal ring 14 is slidably disposed.
  • a resilient seal ring 36 is carried by the rotary seal ring 14 and sealingly engages within the bore 35.
  • an inner peripheral resilient seal ring 37 is carried by the rotary seal ring 14 and sealingly engages about the shaft sleeve 6.
  • a suitable number of circumferentially spaced coiled compression springs 38 is disposed in spring pockets 39 in the spring carrier 30 and engage the end wall 40 of the rotary seal ring 14 so as to normally provide a bias to force the rotary seal ring 14 axially toward the stationary seal ring 13.
  • Means are provided for transmitting rotative movement from the spring carrier 30 to the rotary seal ring 14, and, for this purpose, in the illustrated embodiment, a suitable number of drive pins 41 is disposed in circumferentially spaced pockets 42 in the spring carrier 30 and engaged in sockets 43 in the rotary seal ring 14.
  • the stationary seal ring 13 remains stationary in relation to the rotary seal ring 14 which is driven by the pins 41 in response to the rotation of the pump shaft 3.
  • the seal ring 13 may be appropriately keyed to the flange 17, but in the illustrated embodiment, the ring 13 is press fitted into the bore of the flange 17.
  • the bore 35 of the spring carrier 30 behind the seal ring 14, the spring pockets 39 and drive pin pockets 42 may be packed with a suitable lubricant.
  • the outer periphery 44 of the spring carrier 30 is preferably formed as a frustum of a long cone tapering towards the inner end of the spring carrier 30, whereby the annular space 45 within the stuffing box 2 flares inwardly so as to enhance the displacement of pulp or fibrous material from the space 45 during operation of the seal assembly.
  • the rotary seal ring 14 is biased by the springs 38 toward the stationary seal ring 13 to maintain the sealing correlation between the seal faces 15 and 16.
  • This spring force is supplemented by the pump housing fluid pressure which finds access to the rear face 40 of the rotary seal ring 14 through the gap 33 formed between the spring carrier 30 and the shaft sleeve 6.
  • this gap 33 is so small that fibrous material or the solids in the pulp will not readily pass through the gap.
  • Flushing fluid such as clean pulp liquor or water
  • Flushing fluid is admitted to the inlet passage 23 of the seal flange l7 and flows through the ports or passages 24, 25 26 and 27.
  • This flushing fluid is maintained at a pressure slightly greater than housing or pump fluid pressure so as to maintain a film of flushing fluid flowing between the seal faces 15 and 16.
  • Part ofsuch flushing fluid will flow radially inwardly across the seal faces 15 and 16 and will pass from the assembly through the opening 22 around the sleeve 6, but the remainder of the flushing fluid will flow radially outwardly between the seal faces 15 and 16 into the space 45, and thence it will comingle with the pulp or other liquid in the pump housing.
  • flushing fluid prevents clogging of the mechanical seal by the solid constituents of the pump fluid or pulp, as the flushing fluid flows through the divergent space 45 into the pump housing.
  • the volume of flushing fluid need not be great, so that, when water is employed, the pulp liquor or other fluid in the pump housing is not substantially diluted.
  • FIG. 4 a modified construction is shown.
  • the seal ring 28 of the first described embodiment is eliminated, and instead a flow path 128 is provided for the flow of flushing fluid from the annular passage 24 in the flange 17, along the outer periphery of the stationary seal ring 13.
  • a flow path 128 is provided for the flow of flushing fluid from the annular passage 24 in the flange 17, along the outer periphery of the stationary seal ring 13.
  • the clearance afforded by the space 128 should be sufficiently small as to throttle the flow of flushing fluid therethrough, so that sufficient flushing fluid pressure may be maintained in the annular passage 24 to cause at least some flow between the faces 15 and 16.
  • the bore of the skirt portion 34 of the spring carrier 30 defines with the outer periphery of the shaft sleeve 6 an annular piston chamber.
  • the rotary seal ring 14 with its seal rings 36 and 37, respectively, sealingly engaged within the bore 35 of the skirt 34 and with the shaft sleeve 6 constitutes an annular piston which is spring loaded toward the stationary seal ring 13 by the springs 38.
  • the pressure of fluid in the stufi'mg box 2 finds access through the gap 33 to the piston chamber behind the end wall or face 40 of the rotary seal ring 14 and acts across the effective annular area of the seal ring 14 to force the latter toward the stationary seal ring 13.
  • the gap 33 is small so as to preclude the entry of solid matter into the piston chamber; and when this chamber is filled with a lubricant, the latter serves as a pressure medium and transmits the fluid pressure from the stuffing box 2 to the seal ring face 40, and the lubricant further prevents access of solids into the region of the springs 38.
  • the force acting in the opposite direction to cause the flow of flushing fluid between the seal faces 15 and 16 is a function of the flushing fluid pressure in the circumferentially extended passageways 27. This pressure should be such as to provide a pressure gradient across the seal faces 15 and 16 and such as to maintain the flow of at least a film of the flushing fluid between such seal faces.
  • the present invention provides a mechanical seal assembly which is ideally suited for use in paper pulp pumps, but the seal may also be employed in other applications where there is a likelihood of clogging of the mechanical seal with solids in the pump fluid.
  • a mechanical seal assembly comprising: a stuffing box, a shaft rotatable in said stuffing box, mechanical seal means for sealing said shaft in said stuffing box, said mechanical seal means including a stationary support, a stationary seal ring carried by said support and disposed about said shaft, a rotary seal ring disposed about said shaft, said stationary seal ring and said rotary seal ring having radial seal faces disposed in opposed sealing relation, a spring carrier having an annular body portion disposed about said shaft and an annular skirt portion radially spaced from the outer periphery of said shaft, said rotary seal ring being slidably disposed between said shaft and said skirt, said shaft, said body portion, said skirt and said rotary seal ring defining a substantially closed chamber, means providing a seal between said skirt portion and the outer periphery of said rotary seal ring, means providing a seal between the inner periphery of said rotary seal ring and said shaft, spring means within said chamber, carried by said spring carrier and engaged with said rotary seal ring to bias
  • a mechanical seal assembly as defined in claim 1 wherein said body portion and the inner end of said rotary seal ring define the end walls of said chamber, a drive pin having one end affixed to one of said end walls and the other end slidingly and drivingly engaged with the other of said end walls, a setscrew extending radially through a wall of said spring carrier in driving engagement with said shaft, whereby said shaft, said spring carrier and said rotary seal ring are engaged for rotary movement in concert.
US832967A 1969-06-13 1969-06-13 Mechanical seal for pulp pumps Expired - Lifetime US3589738A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US83296769A 1969-06-13 1969-06-13

Publications (1)

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US3589738A true US3589738A (en) 1971-06-29

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Family Applications (1)

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US832967A Expired - Lifetime US3589738A (en) 1969-06-13 1969-06-13 Mechanical seal for pulp pumps

Country Status (9)

Country Link
US (1) US3589738A (xx)
BR (1) BR7019669D0 (xx)
DE (1) DE2028521A1 (xx)
FR (1) FR2052506A5 (xx)
GB (1) GB1267129A (xx)
NL (1) NL7008511A (xx)
NO (1) NO133417C (xx)
SE (1) SE359360B (xx)
ZA (1) ZA703658B (xx)

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3921986A (en) * 1973-02-28 1975-11-25 Carrier Corp Shaft seal
JPS51156363U (xx) * 1975-06-09 1976-12-13
US4196911A (en) * 1978-05-15 1980-04-08 Tanken Seiko Corp. Mechanical seal
US4215870A (en) * 1978-12-04 1980-08-05 Escue Jesse W Rotatable shaft seal
US4582328A (en) * 1982-03-02 1986-04-15 Mechanical Technology Incorporated Double acting stirling engine piston ring
US4948151A (en) * 1986-10-10 1990-08-14 Atomic Energy Of Canada Limited Rotary end face seal assembly
US4979875A (en) * 1986-10-17 1990-12-25 Sihi Gmbh & Co. Kg Centrifugal pump for the delivery of hot liquids
US5171023A (en) * 1991-02-19 1992-12-15 Scott Robert J Technique for in-place cleaning of a sealing structure
US6059293A (en) * 1997-12-17 2000-05-09 A.W. Chesterton Company Split mechanical face seal with seal face fluid introducing structure
US6068263A (en) * 1997-12-17 2000-05-30 A.W. Chesterton Company Split mechanical face seal with resilient pivoting member
US6068264A (en) * 1997-12-17 2000-05-30 A.W. Chesterton Company Split mechanical face seal with negative pressure control system
US6076830A (en) * 1997-12-17 2000-06-20 A.W. Chesterton Company Dual non-contacting mechanical face seal having concentric seal faces
US6116609A (en) * 1997-12-17 2000-09-12 A. W. Chesterton Company Fluidic feedback pressure regulation system for a mechanical seal
US6131912A (en) * 1997-12-17 2000-10-17 A.W. Chesterton Company Split mechanical face seal
US6135458A (en) * 1997-11-21 2000-10-24 Nippon Pillar Packing Co., Ltd. Static pressure non-contact gas seal
US6142476A (en) * 1996-02-23 2000-11-07 Iwane; Tomoichiro Mechanical seal
US6431551B1 (en) * 1999-08-16 2002-08-13 Nippon Pillar Packing Co., Ltd. Non-contact type mechanical seal
US20030015842A1 (en) * 2001-07-23 2003-01-23 Wilhelm Howard Randall Dry gas shutdown seal
US6517077B1 (en) * 1999-07-05 2003-02-11 M. Technique Co., Ltd. Mechanical seal, and agitating device and process using same
US20030146577A1 (en) * 2002-02-02 2003-08-07 Goldswain Ian Martyn Seals
US20120127825A1 (en) * 2009-08-10 2012-05-24 Jgc Corporation Mechanical seal device and processing apparatus
US20120267860A1 (en) * 2010-03-31 2012-10-25 Eagle Industry Co., Ltd. Pipe connecting mechanism for seal device and mechanical seal device
US10436328B2 (en) 2016-06-10 2019-10-08 John Crane Uk Ltd. Dry gas seal with electronically controlled shutdown valve
US10677357B2 (en) 2017-05-15 2020-06-09 John Crane Uk Ltd. Dry gas seal with electronically controlled carrier load

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2637247C3 (de) 1976-08-19 1981-02-26 Flexibox Gmbh, 6000 Frankfurt Doppeltwirkende Gleitringdichtung
DE2659841C3 (de) * 1976-08-19 1981-03-19 Flexibox Gmbh, 6000 Frankfurt Doppelgleitringdichtung aus Hauptdichtung und Reservedichtung
GB9824724D0 (en) * 1998-11-12 1999-01-06 Pumpmart Limited Sealing assembly

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2902301A (en) * 1955-07-19 1959-09-01 Olin Mathieson Shaft seal
US2971784A (en) * 1955-10-04 1961-02-14 Borg Warner Seal assembly
US3015506A (en) * 1958-03-17 1962-01-02 Borg Warner Multi-step mechanical seal
US3168871A (en) * 1962-07-10 1965-02-09 Roth Co Roy E Means for controlling pressure drop between adjacent chambers of a pump or from insid of pump case to outside atmosphere
FR1418240A (fr) * 1964-10-08 1965-11-19 Rateau Soc Garniture d'étanchéité à barrage par fluide auxiliaire

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2902301A (en) * 1955-07-19 1959-09-01 Olin Mathieson Shaft seal
US2971784A (en) * 1955-10-04 1961-02-14 Borg Warner Seal assembly
US3015506A (en) * 1958-03-17 1962-01-02 Borg Warner Multi-step mechanical seal
US3168871A (en) * 1962-07-10 1965-02-09 Roth Co Roy E Means for controlling pressure drop between adjacent chambers of a pump or from insid of pump case to outside atmosphere
FR1418240A (fr) * 1964-10-08 1965-11-19 Rateau Soc Garniture d'étanchéité à barrage par fluide auxiliaire

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3921986A (en) * 1973-02-28 1975-11-25 Carrier Corp Shaft seal
JPS51156363U (xx) * 1975-06-09 1976-12-13
US4196911A (en) * 1978-05-15 1980-04-08 Tanken Seiko Corp. Mechanical seal
US4215870A (en) * 1978-12-04 1980-08-05 Escue Jesse W Rotatable shaft seal
US4582328A (en) * 1982-03-02 1986-04-15 Mechanical Technology Incorporated Double acting stirling engine piston ring
US4948151A (en) * 1986-10-10 1990-08-14 Atomic Energy Of Canada Limited Rotary end face seal assembly
US4979875A (en) * 1986-10-17 1990-12-25 Sihi Gmbh & Co. Kg Centrifugal pump for the delivery of hot liquids
US5171023A (en) * 1991-02-19 1992-12-15 Scott Robert J Technique for in-place cleaning of a sealing structure
US6142476A (en) * 1996-02-23 2000-11-07 Iwane; Tomoichiro Mechanical seal
US6135458A (en) * 1997-11-21 2000-10-24 Nippon Pillar Packing Co., Ltd. Static pressure non-contact gas seal
US6059293A (en) * 1997-12-17 2000-05-09 A.W. Chesterton Company Split mechanical face seal with seal face fluid introducing structure
US6076830A (en) * 1997-12-17 2000-06-20 A.W. Chesterton Company Dual non-contacting mechanical face seal having concentric seal faces
US6116609A (en) * 1997-12-17 2000-09-12 A. W. Chesterton Company Fluidic feedback pressure regulation system for a mechanical seal
US6120034A (en) * 1997-12-17 2000-09-19 A.W. Chesterston Company Secondary sealing assembly for mechanical face seal
US6131912A (en) * 1997-12-17 2000-10-17 A.W. Chesterton Company Split mechanical face seal
US6068264A (en) * 1997-12-17 2000-05-30 A.W. Chesterton Company Split mechanical face seal with negative pressure control system
US6068263A (en) * 1997-12-17 2000-05-30 A.W. Chesterton Company Split mechanical face seal with resilient pivoting member
US6155572A (en) * 1997-12-17 2000-12-05 A.W. Chesterton Company Non-contacting mechanical face seal including fluid control system
US6386547B2 (en) 1997-12-17 2002-05-14 A. W. Chesterton Company Dual non-contacting mechanical face seal having concentric seal faces
US6557856B1 (en) * 1997-12-17 2003-05-06 A. W. Chesterton Co. Split mechanical face seal
US6517077B1 (en) * 1999-07-05 2003-02-11 M. Technique Co., Ltd. Mechanical seal, and agitating device and process using same
US6431551B1 (en) * 1999-08-16 2002-08-13 Nippon Pillar Packing Co., Ltd. Non-contact type mechanical seal
US20030015842A1 (en) * 2001-07-23 2003-01-23 Wilhelm Howard Randall Dry gas shutdown seal
US6789804B2 (en) * 2001-07-23 2004-09-14 Kaydon Corporation Dry gas shutdown seal
US20030146577A1 (en) * 2002-02-02 2003-08-07 Goldswain Ian Martyn Seals
US6905123B2 (en) * 2002-02-02 2005-06-14 John Crane Uk Limited Seals
US20120127825A1 (en) * 2009-08-10 2012-05-24 Jgc Corporation Mechanical seal device and processing apparatus
US8998213B2 (en) * 2009-08-10 2015-04-07 Jgc Corporation Mechanical seal device and processing apparatus
US20120267860A1 (en) * 2010-03-31 2012-10-25 Eagle Industry Co., Ltd. Pipe connecting mechanism for seal device and mechanical seal device
US8613450B2 (en) * 2010-03-31 2013-12-24 Eagle Industry Co., Ltd. Pipe connecting mechanism for seal device and mechanical seal device
US10436328B2 (en) 2016-06-10 2019-10-08 John Crane Uk Ltd. Dry gas seal with electronically controlled shutdown valve
US10677357B2 (en) 2017-05-15 2020-06-09 John Crane Uk Ltd. Dry gas seal with electronically controlled carrier load
US11015714B2 (en) 2017-05-15 2021-05-25 John Crane Uk Ltd. Dry gas seal with electronically controlled carrier load

Also Published As

Publication number Publication date
NO133417B (xx) 1976-01-19
SE359360B (xx) 1973-08-27
NL7008511A (xx) 1970-12-15
GB1267129A (xx) 1972-03-15
DE2028521A1 (de) 1970-12-17
BR7019669D0 (pt) 1973-02-20
ZA703658B (en) 1971-12-29
NO133417C (xx) 1976-04-28
FR2052506A5 (xx) 1971-04-09

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Legal Events

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AS Assignment

Owner name: CITIBANK, N.A., NEW YORK

Free format text: SECURITY INTEREST;ASSIGNOR:BORG-WARNER INDUSTRIAL PRODUCTS, INC.,;REEL/FRAME:004745/0480

Effective date: 19870520

Owner name: BORG-WARNER INDUSTRIAL PRODUCTS, INC., CALIFORNIA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BORG-WARNER CORPORATION;REEL/FRAME:004745/0469

Effective date: 19870514

Owner name: CITIBANK, N.A., 641 LEXINGTON AVE., NEW YORK, NY 1

Free format text: SECURITY INTEREST;ASSIGNOR:BORG-WARNER INDUSTRIAL PRODUCTS, INC.,;REEL/FRAME:004745/0480

Effective date: 19870520

Owner name: BORG-WARNER INDUSTRIAL PRODUCTS, INC., 200 OCEANGA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:BORG-WARNER CORPORATION;REEL/FRAME:004745/0469

Effective date: 19870514

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Owner name: BW/IP INTERNATIONAL, INC., ("BW/IP"),A CORP. OF DE

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BORG-WARNER CORPORATION, A DE. CORP.;REEL/FRAME:004836/0834

Effective date: 19880215

Owner name: BW/IP INTERNATIONAL, INC., ("BW/IP"), 200 OCEANGAT

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST. EFFECTIVE MAY 20, 1987;ASSIGNOR:BORG-WARNER CORPORATION, A DE. CORP.;REEL/FRAME:004836/0834

Effective date: 19880215

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Owner name: CITIBANK, N.A., NEW YORK

Free format text: RELEASED BY SECURED PARTY;ASSIGNOR:BW/IP INTERNATIONAL INC. (FORMERLY KNOWN AS BORG-WARNER INDUSTRIAL PRODUCTS, INC.);REEL/FRAME:006376/0881

Effective date: 19910831