US20010002742A1 - Shaft seal assembly - Google Patents

Shaft seal assembly Download PDF

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Publication number
US20010002742A1
US20010002742A1 US09/139,499 US13949998A US2001002742A1 US 20010002742 A1 US20010002742 A1 US 20010002742A1 US 13949998 A US13949998 A US 13949998A US 2001002742 A1 US2001002742 A1 US 2001002742A1
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US
United States
Prior art keywords
stator
rotor
seal
shaft
projection
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.)
Granted
Application number
US09/139,499
Other versions
US6419233B2 (en
Inventor
David C. Orlowski
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.)
H VICENT HARSHA
VICENT HARSHA H
Inpro Seal LLC
Original Assignee
Individual
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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=22486956&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=US20010002742(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Individual filed Critical Individual
Priority to US09/139,499 priority Critical patent/US6419233B2/en
Assigned to INPRO COMPANIES, INC. reassignment INPRO COMPANIES, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ORLOWSKI, DAVID C.
Assigned to ISOTECH OF ILLINOIS, INC. reassignment ISOTECH OF ILLINOIS, INC. CORRECTIVE ASSIGNMENT TO CORRECT THE NAME OF THE RECEIVING PARTY PREVIOUSLY RECORDED ON REEL 9699 FRAME 0861. Assignors: ORLOWSKI, DAVID C.
Priority to JP2000566600A priority patent/JP3827950B2/en
Priority to CA002306834A priority patent/CA2306834C/en
Priority to DE69941893T priority patent/DE69941893D1/en
Priority to DK99942419.5T priority patent/DK1053421T3/en
Priority to ES99942419T priority patent/ES2338617T3/en
Priority to BR9906898-2A priority patent/BR9906898A/en
Priority to AT99942419T priority patent/ATE454580T1/en
Priority to PCT/US1999/019155 priority patent/WO2000011380A1/en
Priority to EP99942419A priority patent/EP1053421B8/en
Priority to AU55803/99A priority patent/AU740388B2/en
Priority to PT99942419T priority patent/PT1053421E/en
Priority to ZA200001985A priority patent/ZA200001985B/en
Publication of US20010002742A1 publication Critical patent/US20010002742A1/en
Publication of US6419233B2 publication Critical patent/US6419233B2/en
Application granted granted Critical
Assigned to WAUKESHA ACQUISITION, LLC reassignment WAUKESHA ACQUISITION, LLC ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: COJEN HOLDINGS, L.L.C., INPRO/SEAL CO., ISOTECH OF ILLINOIS, INC.
Assigned to INPRO/SEAL LLC reassignment INPRO/SEAL LLC CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: WAUKESHA ACQUISITION, LLC
Priority to CY20101100290T priority patent/CY1110908T1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F16J15/44—Free-space packings
    • F16J15/447—Labyrinth packings
    • F16J15/4476—Labyrinth packings with radial path
    • F16J15/4478—Pre-assembled packings

Definitions

  • This invention relates generally to shaft sealing devices for use with rotating equipment. Adequate maintenance of rotating equipment is difficult to obtain because of extreme equipment duty cycles, the lessening of service factors, design and the lack of spare rotating equipment in many processing plants. This is especially true of machine tool spindles, wet end paper machine rolls, aluminum rolling mills and steam quench pumps and other equipment utilizing extreme contamination affecting lubrication.
  • Labyrinth-type seals involving closely related stator and rotor rings, which do not contact each other but define labyrinth passages between them have been devised and utilized and are illustrated in Orlowski, U.S. Pat. Nos. 4,706,968; 4,989,883; 5,069,461; and the additional patents to Orlowski cited therein.
  • improvements in labyrinth seals are disclosed including the utilization of various forms of O-ring seals to improve the static sealing action when the shaft is at rest and non-contact dynamic sealing action is provided when the shaft is rotating.
  • An objective of the present invention is to provide an improvement to seals or bearing isolators to prevent leakage of lubricant and entry of contaminants by encompassing the stator within the rotor to create an axial directed interface at the radial extremity of the rotor.
  • Prior art seals traditionally had the interface between the rotor and the stator exposed radially to the contaminants or lubricants at the radial extremity of the seal.
  • the rotor and the recess in the rotor which previously surrounded the stator projection or insertion, is also extended radially beyond the major portion of the stator.
  • the rotor now encompasses the stator, or a substantial portion of the stator projection, in such a manner that the interface presented to the ingress of the lubricant or contaminates is facing axially and rearwardly.
  • the axial facing interface presents a limited access to the internal of the seal and a constant dimensional interface between the rotor and the stator regardless of any axial movement of the rotor with respect to the stator.
  • a groove may be machined into the stator to accentuate the novel radial extension of the rotor and the stator. This groove improves the ability of the seal to prevent contaminates from entering the axial interface gap between the rotor and the stator.
  • This novel improvement i.e. the encapsulation of the stator by the rotor enables the interface gap between the accessible portions of the stator and the rotor to be of a predetermined dimension.
  • the improvement also means that there is no fluctuation or variation in the interface gap resulting from any relative axial movement between the rotor and the stator.
  • This novel seal or bearing isolator will operate to vastly improve the rejection or ingress of contaminants into the interface gap between the rotor and stator.
  • the entrance to the interface gap is facing or directed away from the normal flow of contaminants i.e. along the axis of the shaft toward the housing.
  • the interface gap can be machined to extremely close tolerances because there is no movement radially between the rotor and the stator and any axial movement does not affect the interface.
  • FIG. 1 is a sectional view showing the sealing structure of the prior art with a shaft.
  • FIG. 2 is a sectional view showing the improved sealing structure of this invention with a shaft.
  • FIG. 1 shows the prior art having the most control over the relative axial movement between rotor and stator.
  • the prior art essentially had the interfacing gap opening radially into the lubrication or contaminant substantially as shown in FIG. 1.
  • the novelty of this invention is as shown in FIG. 2 and as described herein.
  • the invention can also be utilized on seals or bearing isolators using only labyrinths as shown in much of the prior art referenced.
  • Radial interface gap 21 is also receptive to contaminants, especially in extreme conditions presented to the surfaces 13 a and 14 a of the rotor 13 and the stator 14 regardless of the dimension of the interface gap 21 .
  • this invention extends the rotor 13 radially well beyond the major diameter of the stator 14 . This permits the rotor 13 to encompass the also radially extended projection 19 of the stator 14 . It is important that this radial extension of the rotor 13 extends beyond the basic radial dimension of stator 14 . This requires a departure from the prior art wherein the rotor 13 was radially co-extensive with the major diameter of the stator 14 .
  • the interface gap 21 between the rotor 13 and stator 14 that is exposed to the contamination or lubricants is now fixed in dimension and independent of any relative axial movement between the rotor 13 and the stator 14 .
  • the interface gap 20 is still subject to variation in dimension by any relative movement between the rotor 13 and the stator 14 . This relative movement is not significant to the operation in as much as only a small amount of contaminates have been able to enter the labyrinth because of size and location of the interface gap.
  • the removal of the interface gap 21 from variations is more important in seals where the stator 13 and the rotor 14 are not restrained from relative movement.
  • the orientation of the opening of the interface gap of 21 is important regardless of relative movement between the rotor and stator.
  • the interface gap 21 being axially oriented to control entrance of contaminates is novel and important.
  • the opening of the interface gap 21 is now facing rearwardly toward the housing and away from the contaminates stream.
  • the contaminate or cooling stream will normally be directed along the axis of the shaft 10 and toward the housing 11 .
  • a groove 22 may be cut in stator 14 . This groove 22 enhances and accentuates the benefits of the radial extension of the rotor 13 and the stator 14 with the resultant orientation and independence of interface gap 21 .
  • This seal may be made from any machinable metal such as bronze or stainless steel or machineable plastics such as Teflon® or other machinable plastics.

Abstract

An improved shaft seal assembly is disclosed having a stator including a main body and axial and radial projections therefrom. The rotor is radially extended and encompasses the axial and radial projections from said stator. The passageway formed between the radial projection of the stator and the rotor results in an axial passageway having its opening facing rearwardly from the rotor and away from the source of impinging coolant and/or contaminant. The dimension of interface gap between the rotor and the radial projection from the stator, which the access to the shaft of any impinging material, is fixed at a predetermined value and does not vary with the relative movement between the rotor and the stator. The novel seal assembly of this invention thus provides improved rejection or warding off of contaminates from ingress into the labyrinths and ultimately restrained from attacking the bearing environment.

Description

    BACKGROUND OF THE INVENTION
  • This invention relates generally to shaft sealing devices for use with rotating equipment. Adequate maintenance of rotating equipment is difficult to obtain because of extreme equipment duty cycles, the lessening of service factors, design and the lack of spare rotating equipment in many processing plants. This is especially true of machine tool spindles, wet end paper machine rolls, aluminum rolling mills and steam quench pumps and other equipment utilizing extreme contamination affecting lubrication. [0001]
  • Various forms of shaft sealing devices have been utilized to try to protect the integrity of the bearing environment, including rubber lip seals, clearance labyrinth seals, and attraction magnetic seals. Lip seals or O-ring shaft seals can quickly wear out and fail and are also known to permit excessive amounts of moisture and other contaminants to immigrate into oil reservoir of the operating equipment even before failure had the interface between the rotor and the stator exposed to the contaminates or lubricants at the radial extremity of the seal. [0002]
  • Labyrinth-type seals involving closely related stator and rotor rings, which do not contact each other but define labyrinth passages between them have been devised and utilized and are illustrated in Orlowski, U.S. Pat. Nos. 4,706,968; 4,989,883; 5,069,461; and the additional patents to Orlowski cited therein. As described in Orlowski U.S. Pat. Nos. 4,989,883 and 5,069,461, improvements in labyrinth seals are disclosed including the utilization of various forms of O-ring seals to improve the static sealing action when the shaft is at rest and non-contact dynamic sealing action is provided when the shaft is rotating. [0003]
  • An improvement over these labyrinth seals and o-ring seals is described in U.S. Pat. No. 5,378,000. There the isolator or seal provides a sealing ring inserted in recesses in the rotor and the stator to lock together the rotor and stator in an axial direction. This actual lock up of rotor and stator dramatically reduces the possibility of migration of rotor from stator. The resultant is a reduced radial interface gap variation from that which had existed previously between the rotor and the stator. [0004]
  • An objective of the present invention is to provide an improvement to seals or bearing isolators to prevent leakage of lubricant and entry of contaminants by encompassing the stator within the rotor to create an axial directed interface at the radial extremity of the rotor. Prior art seals traditionally had the interface between the rotor and the stator exposed radially to the contaminants or lubricants at the radial extremity of the seal. [0005]
  • The projection of an axial portion of the stator into the rotor has been expanded radially. This projection or protruding member of the stator into the rotor has been expanded radially beyond the diameter of the major portion or body of the stator. [0006]
  • The rotor and the recess in the rotor, which previously surrounded the stator projection or insertion, is also extended radially beyond the major portion of the stator. The rotor now encompasses the stator, or a substantial portion of the stator projection, in such a manner that the interface presented to the ingress of the lubricant or contaminates is facing axially and rearwardly. The axial facing interface presents a limited access to the internal of the seal and a constant dimensional interface between the rotor and the stator regardless of any axial movement of the rotor with respect to the stator. [0007]
  • A groove may be machined into the stator to accentuate the novel radial extension of the rotor and the stator. This groove improves the ability of the seal to prevent contaminates from entering the axial interface gap between the rotor and the stator. [0008]
  • This novel improvement i.e. the encapsulation of the stator by the rotor enables the interface gap between the accessible portions of the stator and the rotor to be of a predetermined dimension. The improvement also means that there is no fluctuation or variation in the interface gap resulting from any relative axial movement between the rotor and the stator. [0009]
  • This novel seal or bearing isolator will operate to vastly improve the rejection or ingress of contaminants into the interface gap between the rotor and stator. The entrance to the interface gap is facing or directed away from the normal flow of contaminants i.e. along the axis of the shaft toward the housing. The interface gap can be machined to extremely close tolerances because there is no movement radially between the rotor and the stator and any axial movement does not affect the interface. [0010]
  • Other objects, advantages embodiments of the invention will become apparent upon the reading the following detailed description and upon reference to drawings and the prior art patents. [0011]
    • BRIEF DESCRIPTION OF THE DRAWINGS
  • FIG. 1 is a sectional view showing the sealing structure of the prior art with a shaft. [0012]
  • FIG. 2 is a sectional view showing the improved sealing structure of this invention with a shaft. [0013]
    • DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT OF THE INVENTION
  • FIG. 1 shows the prior art having the most control over the relative axial movement between rotor and stator. The prior art essentially had the interfacing gap opening radially into the lubrication or contaminant substantially as shown in FIG. 1. [0014]
  • The novelty of this invention is as shown in FIG. 2 and as described herein. The invention can also be utilized on seals or bearing isolators using only labyrinths as shown in much of the prior art referenced. [0015]
  • It should be noted, as shown in FIG. 2, that the location of the gap with respect to rotor and stator surfaces and the direction of the opening interface gap are both important to this invention. [0016]
  • In FIG. 1, axial movement of the [0017] rotor 13 relative to the stator 14 will change the size of the radial interface gaps 20 and 21. Radial interface gap 21 is also receptive to contaminants, especially in extreme conditions presented to the surfaces 13 a and 14 a of the rotor 13 and the stator 14 regardless of the dimension of the interface gap 21.
  • As shown in FIG. 2 this invention extends the [0018] rotor 13 radially well beyond the major diameter of the stator 14. This permits the rotor 13 to encompass the also radially extended projection 19 of the stator 14. It is important that this radial extension of the rotor 13 extends beyond the basic radial dimension of stator 14. This requires a departure from the prior art wherein the rotor 13 was radially co-extensive with the major diameter of the stator 14.
  • The [0019] interface gap 21 between the rotor 13 and stator 14 that is exposed to the contamination or lubricants is now fixed in dimension and independent of any relative axial movement between the rotor 13 and the stator 14. The interface gap 20 is still subject to variation in dimension by any relative movement between the rotor 13 and the stator 14. This relative movement is not significant to the operation in as much as only a small amount of contaminates have been able to enter the labyrinth because of size and location of the interface gap. The removal of the interface gap 21 from variations is more important in seals where the stator 13 and the rotor 14 are not restrained from relative movement.
  • The orientation of the opening of the interface gap of [0020] 21 is important regardless of relative movement between the rotor and stator. The interface gap 21 being axially oriented to control entrance of contaminates is novel and important. The opening of the interface gap 21 is now facing rearwardly toward the housing and away from the contaminates stream. The contaminate or cooling stream will normally be directed along the axis of the shaft 10 and toward the housing 11.
  • A groove [0021] 22 may be cut in stator 14. This groove 22 enhances and accentuates the benefits of the radial extension of the rotor 13 and the stator 14 with the resultant orientation and independence of interface gap 21.
  • This seal may be made from any machinable metal such as bronze or stainless steel or machineable plastics such as Teflon® or other machinable plastics. [0022]
  • Variations and other aspects of the preferred embodiment will occur to those versed in the art all without departure from the spirit and scope of the invention. [0023]

Claims (17)

What is claimed:
1. A seal for sealing a rotating shaft entering a housing comprising:
a. a stator surrounding a shaft and affixed to a housing, said stator having a main body and a projection extending both axially and radially beyond said main body;
b. a rotor surrounding said shaft and rotatively connected to said shaft;
c. said rotor and said stator abutting each other on said shaft;
d. said rotor encompassing said projection of said stator.
2. A seal, according to
claim 1
 wherein said rotor axially and radially extends beyond said projection on said stator.
3. A seal, according to
claim 1
, wherein the space between said rotor and said stator projection forms passages.
4. A seal, according to
claim 3
, wherein said passages include an axial passage opening to the space between said housing and radial extension of the rotor and stator.
5. A seal, in accordance to
claim 3
, wherein dimension of said axial passage is constant.
6. A seal, in accordance to
claim 5
, wherein the dimension of said axial passage is predetermined.
7. A seal, in accordance to
claim 4
, wherein said opening of said axial passage faces the stator.
8. A seal, in accordance to
claim 4
, wherein said opening of said axial passage faces away from said coolant, said rotor and towards said housing.
9. A seal, according to
claim 1
, wherein there is at least one labyrinth formed between the main body of said stator and said rotor.
10. A seal, according to
claim 1
, wherein said rotor and said stator are restrained from relative axial movement between each other.
11. A seal, according to
claim 1
, wherein a groove is formed in said main body of said stator, said groove augmenting the radial extension of said projection from said stator.
12. A seal, according to
claim 1
, wherein a groove formed in said body of said stator, augments the axial extension of said projection of said body of said stator.
13. A seal, according to
claim 2
, wherein said main body of said stator surrounds a portion of said rotor.
14. A seal, according to
claim 3
, wherein the radius of the radial internal surface of the rotor encompassing said stator is greater than the radius of the exterior surface of said radial projection of said stator.
15. A method of sealing a shaft exit a housing, the method comprising:
a. fixing a stator having a main body and a projection extending both radially and axially beyond the main body of said stator to the housing concentrically about the shaft;
b. mounting a rotor sealed on the shaft in close relation to the housing for rotation with the shaft;
c. the rotor encompassing the radially extremity of the radial projection of the stator and having overlapping radially spaced surfaces forming an axial passage between the surfaces of the rotor and the stator extension;
d. the opening of said axial passage faced away from said rotor and toward the body of said stator.
16. The method of
claim 15
, including at least one labyrinth between the rotor and the main body of the stator.
17. The method of
claim 15
, including the steps of rotatively connecting the stator to the rotor to prevent relative axial movement between the stator and the rotor.
US09/139,499 1998-08-25 1998-08-25 Shaft seal assembly Expired - Lifetime US6419233B2 (en)

Priority Applications (14)

Application Number Priority Date Filing Date Title
US09/139,499 US6419233B2 (en) 1998-08-25 1998-08-25 Shaft seal assembly
PT99942419T PT1053421E (en) 1998-08-25 1999-08-24 Improved shaft seal assembly
CA002306834A CA2306834C (en) 1998-08-25 1999-08-24 Improved shaft seal assembly
PCT/US1999/019155 WO2000011380A1 (en) 1998-08-25 1999-08-24 Improved shaft seal assembly
AU55803/99A AU740388B2 (en) 1998-08-25 1999-08-24 Improved shaft seal assembly
DE69941893T DE69941893D1 (en) 1998-08-25 1999-08-24 SHAFT SEAL
DK99942419.5T DK1053421T3 (en) 1998-08-25 1999-08-24 Improved shaft seal assembly
ES99942419T ES2338617T3 (en) 1998-08-25 1999-08-24 ASSEMBLY OF BOARD FOR IMPROVED TREE.
BR9906898-2A BR9906898A (en) 1998-08-25 1999-08-24 Improved shaft seal assembly
AT99942419T ATE454580T1 (en) 1998-08-25 1999-08-24 SHAFT SEAL
JP2000566600A JP3827950B2 (en) 1998-08-25 1999-08-24 Shaft sealing device
EP99942419A EP1053421B8 (en) 1998-08-25 1999-08-24 Improved shaft seal assembly
ZA200001985A ZA200001985B (en) 1998-08-25 2000-04-19 Improved shaft seal assembly.
CY20101100290T CY1110908T1 (en) 1998-08-25 2010-03-29 ASSEMBLING OF IMPROVED SHAPE SEAL

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US09/139,499 US6419233B2 (en) 1998-08-25 1998-08-25 Shaft seal assembly

Publications (2)

Publication Number Publication Date
US20010002742A1 true US20010002742A1 (en) 2001-06-07
US6419233B2 US6419233B2 (en) 2002-07-16

Family

ID=22486956

Family Applications (1)

Application Number Title Priority Date Filing Date
US09/139,499 Expired - Lifetime US6419233B2 (en) 1998-08-25 1998-08-25 Shaft seal assembly

Country Status (14)

Country Link
US (1) US6419233B2 (en)
EP (1) EP1053421B8 (en)
JP (1) JP3827950B2 (en)
AT (1) ATE454580T1 (en)
AU (1) AU740388B2 (en)
BR (1) BR9906898A (en)
CA (1) CA2306834C (en)
CY (1) CY1110908T1 (en)
DE (1) DE69941893D1 (en)
DK (1) DK1053421T3 (en)
ES (1) ES2338617T3 (en)
PT (1) PT1053421E (en)
WO (1) WO2000011380A1 (en)
ZA (1) ZA200001985B (en)

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US20040070150A1 (en) * 2002-09-30 2004-04-15 Elizabeth Chitren Unitizing element and method for assembling a seal
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US20140064936A1 (en) * 2011-01-28 2014-03-06 Aktiebolaget Skf Reinforced seal for rotary shafts
US20140361490A1 (en) * 2011-12-19 2014-12-11 Aktiebolaget Skf Pressure Resistant Static and Dynamic Seal Assembly and Method
US20140374993A1 (en) * 2011-12-19 2014-12-25 Aktiebolaget Skf Pressure Resistant Static and Dynamic Seal Assembly and Method
US9140366B2 (en) * 2014-01-10 2015-09-22 Flowserve Management Company Bearing isolator seal for rotating shaft
JP2016512870A (en) * 2013-03-17 2016-05-09 パウル ミュラー ゲーエムベーハー ウント コンパニー カーゲー ウンターネーメンスベタイリグンゲン Sealing element
US9587743B2 (en) * 2012-02-10 2017-03-07 Orion Engineered Seals, Llc Labyrinth seal
US10203036B2 (en) * 2015-06-18 2019-02-12 Inpro/Seal Llc Shaft seal assembly
US10704692B1 (en) 2017-04-26 2020-07-07 Garlock Sealing Technologies, Llc Flooded metallic bearing isolator
US10753478B2 (en) 2016-11-07 2020-08-25 Garlock Sealing Technologies, Llc Bearing isolator for extreme conditions

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US9709172B2 (en) 2013-12-02 2017-07-18 Farrel Corporation Rotor shaft seal assembly
US9917491B2 (en) 2014-03-07 2018-03-13 Nidec Motor Corporation Ground ring and enclosure in an electric motor
US10927961B2 (en) 2015-04-21 2021-02-23 Inpro/Seal Llc Shaft seal assembly
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US6062568A (en) * 1997-07-10 2000-05-16 Orlowski; David C. Bearing isolator with air purge
US6234489B1 (en) * 1999-02-05 2001-05-22 Isotech Of Illinois, Inc. Bearing isolator

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US20060087084A1 (en) * 2002-09-30 2006-04-27 Garlock Sealing Technologies Llc Unitizing element and method for assembling a seal
US7201377B2 (en) 2002-09-30 2007-04-10 Garlock Sealing Technologies Llc Unitizing element and method for assembling a seal
US20080001362A1 (en) * 2002-09-30 2008-01-03 Garlock Sealing Technologies Split bearing isolator and a method for assembling seal
US7427070B2 (en) 2002-09-30 2008-09-23 Garlock Sealing Technologies Llc Unitizing element and method for assembling a seal
US7604239B2 (en) 2002-09-30 2009-10-20 Garlock Scaling Technologies LLC Split bearing isolator and a method for assembling seal
US20040070150A1 (en) * 2002-09-30 2004-04-15 Elizabeth Chitren Unitizing element and method for assembling a seal
US20090096627A1 (en) * 2006-09-07 2009-04-16 Orlowski David C Bearing Monitoring Method
US7839294B2 (en) * 2006-09-07 2010-11-23 Inpro/Seal, LLC Bearing monitoring method
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US8820749B2 (en) 2009-11-11 2014-09-02 Garlock Sealing Technologies, Llc Flooded bearing isolator
US20110109047A1 (en) * 2009-11-11 2011-05-12 Garlock Sealing Technologies, Llc Flooded bearing isolator
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US20140064936A1 (en) * 2011-01-28 2014-03-06 Aktiebolaget Skf Reinforced seal for rotary shafts
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US20220025974A1 (en) * 2012-02-10 2022-01-27 Orion Engineered Seals, Llc Labyrinth seal
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US20170159825A1 (en) * 2012-02-10 2017-06-08 Orion Engineered Seals, Llc Labyrinth seal
US20180238453A1 (en) * 2012-02-10 2018-08-23 Orion Engineered Seals, Llc Labyrinth seal
US11761543B2 (en) * 2012-02-10 2023-09-19 Orion Engineered Seals, Llc Labyrinth seal
JP2016512870A (en) * 2013-03-17 2016-05-09 パウル ミュラー ゲーエムベーハー ウント コンパニー カーゲー ウンターネーメンスベタイリグンゲン Sealing element
CN103291641A (en) * 2013-05-16 2013-09-11 安徽三环水泵有限责任公司 Mining special multistage centrifugal pump
US9140366B2 (en) * 2014-01-10 2015-09-22 Flowserve Management Company Bearing isolator seal for rotating shaft
US11002362B2 (en) * 2015-06-18 2021-05-11 Inpro/Seal Llc Shaft seal assembly
US10203036B2 (en) * 2015-06-18 2019-02-12 Inpro/Seal Llc Shaft seal assembly
US10753478B2 (en) 2016-11-07 2020-08-25 Garlock Sealing Technologies, Llc Bearing isolator for extreme conditions
US10704692B1 (en) 2017-04-26 2020-07-07 Garlock Sealing Technologies, Llc Flooded metallic bearing isolator
US11365810B1 (en) 2017-04-26 2022-06-21 Garlock Sealing Technologies, Llc Flooded metallic bearing isolator

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EP1053421A1 (en) 2000-11-22
DK1053421T3 (en) 2010-04-26
JP3827950B2 (en) 2006-09-27
JP2002523700A (en) 2002-07-30
EP1053421B8 (en) 2010-03-10
CA2306834A1 (en) 2000-03-02
CY1110908T1 (en) 2015-06-10
BR9906898A (en) 2002-01-15
DE69941893D1 (en) 2010-02-25
ZA200001985B (en) 2000-11-01
AU740388B2 (en) 2001-11-01
ES2338617T3 (en) 2010-05-10
EP1053421A4 (en) 2004-03-24
US6419233B2 (en) 2002-07-16
CA2306834C (en) 2006-05-09
WO2000011380A1 (en) 2000-03-02
PT1053421E (en) 2010-03-04
EP1053421B1 (en) 2010-01-06
ATE454580T1 (en) 2010-01-15

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