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WO1999031411A1 - Ensemble joint mecanique a bagues de charge cooperant avec des bagues d'etancheite - Google Patents

Ensemble joint mecanique a bagues de charge cooperant avec des bagues d'etancheite Download PDF

Info

Publication number
WO1999031411A1
WO1999031411A1 PCT/US1998/026332 US9826332W WO9931411A1 WO 1999031411 A1 WO1999031411 A1 WO 1999031411A1 US 9826332 W US9826332 W US 9826332W WO 9931411 A1 WO9931411 A1 WO 9931411A1
Authority
WO
WIPO (PCT)
Prior art keywords
seal
ring
load
rings
seal ring
Prior art date
Application number
PCT/US1998/026332
Other languages
English (en)
Inventor
Michael D. Anderson
Billy R. Bedford
Joseph A. Blandino
Eldon W. Brasche
Michael D. Hasselbusch
Aaron L. Smith
Original Assignee
Caterpillar 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 Caterpillar Inc. filed Critical Caterpillar Inc.
Publication of WO1999031411A1 publication Critical patent/WO1999031411A1/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
    • F16J15/3436—Pressing means
    • F16J15/344—Pressing means the pressing force being applied by means of an elastic ring supporting the slip-ring

Definitions

  • This invention relates generally to a metal -to- metal face seal assembly and more particularly to such a seal assembly having a load ring which interfits with the seal ring to prevent relative rotation between the load ring and the seal ring.
  • Known face seal assemblies for use in constructions having relatively rotating components typically comprise a pair of confronting seal rings of metal or other durable, hard material.
  • the seal rings rotate relative to one another in face-to-face contact to provide a positive face seal which retains lubricant and prevents foreign matter from reaching the internal bearing surfaces of the rotating assembly.
  • Contact between the seal faces is maintained by a pair of resilient load rings which engage and press against each seal ring to thereby force the seal faces against one another.
  • the coefficient of friction between the seal faces may be higher than the coefficient of friction between a seal ring and its corresponding load ring, in which case relative rotation or slippage between one or both of the seal rings and its corresponding load ring may occur.
  • slippage could occur, for example, if the faces of the confronting seal rings stick together due to icing or the like or if the engaging surfaces of the seal ring and load ring become lubricated. Slippage of the load ring relative to the seal ring results in a temporary loss of sealing protection, which can permit dirt and other abrasives to reach the internally lubricated bearings of the rotating assembly.
  • This invention is directed to overcoming one or more of the problems set forth above.
  • a seal assembly in accordance this invention comprises first and second seal rings having mutually- confronting annular seal faces and first and second corresponding load rings each adapted to engage and apply force to its corresponding seal ring to thereby maintain the seal faces in sealing engagement.
  • Each of the load rings has an annular surface which engages an annular surface of its corresponding seal ring.
  • the mutually-engaging annular surfaces of at least one of the seal rings and its corresponding load ring are configured such that aligned portions thereof interfit within one another to thereby resist relative rotation between the at least one seal ring and its corresponding load ring.
  • the annular surface of at least one of the seal rings has a plurality of circumferentially-spaced splines engaging the confronting annular surface of its corresponding load ring.
  • the annular surface of at least one of the load rings has a plurality of circumferentially-spaced splines engaging the confronting annular surface of its corresponding seal ring.
  • FIG. 1 is a diagrammatic, partially cross- sectional view of a track roller assembly incorporating a pair of seal assemblies in accordance with this invention.
  • FIG. 2 is an enlarged cross-sectional view of a portion of one of the seal assemblies illustrated in FIG. 1.
  • FIG. 3 is a perspective view of a seal ring forming part of the seal assembly shown in FIGS. 1 and 2.
  • FIG. 4 is a perspective view of the load ring illustrated in FIG. 3.
  • FIG. 5 is a fragmentary cross-sectional view taken along line 5 - 5 of FIG. 2 showing mutually interfitting portions of the seal ring and the load ring.
  • FIG. 6 is a cross-sectional view similar to FIG. 2 but showing a second embodiment of a seal assembly in accordance with this invention.
  • FIG. 7 is a fragmentary cross-sectional view of the seal assembly of claim 6 taken along line 7 - 7 thereof showing mutually interfitting portions of the seal ring and the load ring.
  • the track roller assembly 10 includes a central supporting shaft 12, first and second bushings 14,16, a roller shell 18, first and second end caps 20,22, first and second seal assemblies 24,26, and first and second split metal retaining rings 28,30 which secure the roller shell 18 in a fixed position with respect to the bushings 14,16 and the shaft 12.
  • the first and second end caps 20,22 are preferably press-fitted to the shaft 12 and the first and second bushings 14,16 are preferably press-fitted to the roller shell 18.
  • the supporting shaft 12 has first and second end portions 32,34, a central flange portion 36, and first and second bushing supporting portions 38,40 which are positioned respectively between the central flange portion 36 and the first and second end portions 32,34.
  • the first and second bushings 14,16 are positioned on respective first and second bushing supporting portions 38,40 of the supporting shaft 12.
  • the roller shell 18 has first and second tread portions 42,44 and an internal through bore 46 with the supporting shaft 12 and bushings 14,16 being adapted to fit within the bore 46.
  • the tread portions 42,44 have respective contact surfaces 48,50 which are adapted to contact the endless track (not shown) of the track-type machine (not shown) .
  • the first and second end caps 20,22 are positioned on respective first and second shaft end portions 32,34 and substantially close off each end of the internal bore 46.
  • the first and second seal assemblies 24,26 are positioned between respective first and second bushings 14,16 and first and second end caps 20,22. The seal assemblies 24,26 prevent leakage of lubricating fluid out of the internal bore 46 and prevent dirt and other foreign material from entering the internal bore 46.
  • the track roller shell 18 has first and second circular grooves 52,54 formed in the internal bore 46 and the split retaining rings 28,30 are adapted to fit within respective grooves 52,54.
  • Each of the bushings 14,16 has first and second end portions 56,58 with the first end portions 56 being adapted to contact one of the split rings 28,30 and the second end portions 58 being adapted to contact the central flange portion 36 of the supporting shaft 12.
  • the track roller assembly 10 further includes first .and second bearing sleeves 60,62, with each sleeve 60,62 having a radially extending flange portion 64.
  • the bearing sleeves 60,62 are positioned between the respective first and second bushing supporting portions 38,40 and the first and second bushings 14,16.
  • the flange portion 64 of each sleeve 60,62 is positioned between the central flange portion 36 of the shaft 12 and the second end portion 58 of one of the bushings 14,16.
  • Each of the seal assemblies 24,26 includes first and second metal seal rings 66,68 and first and second resilient load rings 70,72.
  • the seal rings 66,68 are substantially similar with each seal ring 66,68 having a seal face 74 which mates with a like seal face 74 on a mating seal ring 66,68 in the assembled condition of the seal assembly 24,26.
  • the resilient load rings 70,72 are also substantially similar and are adapted to apply a force to the seal rings 66,68 and the seal faces 74.
  • Each of the resilient load rings 70,72 is cup-shaped, is columnar in cross-section, and is configured similar to the load rings described in the aforementioned 5,527,046 patent. The manner in which the seal faces 74 are maintained in sealing engagement by the load rings 70, 72 is well known in the art and is not described further herein.
  • the load rings 70, 72 are configured such that portions of each load ring 70,72 interfits with aligned portions of its corresponding seal ring 66, 68, as will be described in greater detail below, to thereby resist relative rotation between the load rings 70,72 and their corresponding seal rings 66, 68.
  • the load rings 70, 72 are preferably formed by compression molding using a two-piece mold.
  • FIGS. 3 and 4 illustrate the seal ring 66 and the load ring 70 of the seal assembly 24 configured in accordance with this invention. Because the confronting seal ring 68 and corresponding load ring 72 of the seal assembly 24 may be substantially identical, further discussion is limited to the seal ring 66 and the load ring 70.
  • the seal ring 66 is provided with a plurality of circumferentially-spaced splines 100 around the outer annular surface 102 thereof. The splines 100 creates a series of peaks and valleys along the annular surface 102. As shown in FIG.
  • the load ring 70 is provided with a corresponding number of circumferentially-spaced splines 104 around the inner annular surface 106 thereof, thereby creating a series of peaks and valleys along the annular surface 106.
  • the splines 104 of the load ring 70 are offset from the splines 100 of the seal ring 66 so that, when the load ring 70 is fitted onto the seal ring 66, the peaks along the annular surface 106 are aligned with the valleys along the annular surface 102, and vice versa.
  • the splines 100, 104 are configured such that the shape of each valley conforms to the shape of its aligned peak, and vice versa, as best shown in FIG. 5.
  • the interfitting relationship of the splines 100, 102 creates an interference fit between the load ring 70 and the seal ring 66, which resists rotation of the load ring 70 relative to the seal ring 66.
  • the illustrated seal ring 66 and load ring 70 are such that the splines 100 of the seal ring 66 project generally radially outwardly and the splines 104 of the seal ring 70 project generally radially inwardly.
  • FIGS. 6 and 7 illustrate another embodiment of a seal assembly, generally designated 124, in accordance with this invention which incorporates additional means to resist rotation of the load rings relative to the seal rings.
  • the seal assembly 124 and surrounding structure may be identical to the seal assembly 24 described above. Therefore, like part are given like reference numbers but increased by 100.
  • each seal ring 166, 168 is formed with an open circumferential channel 300, 302 which receives an end portion of the corresponding load ring 170,172.
  • the illustrated channel 300 has a radially-inwardly facing side wall 304 opposite the splines 200 which, as will be described, serves as a retaining wall.
  • each of the splines 204 on the load ring 170 must move over its adjacent spline 100 on the seal ring 166.
  • One way this may occur is by radial stretching or expansion of the load ring 170, but such expansion is prevented by the retaining side wall 304 of the channel 300.
  • the channel 300 cooperates with the splines 200 to further resist rotation of the load ring 170 relative to the seal ring 166.
  • channels 300,302 on the seal ring 166,168 is particularly suited for final drive environments or other environments wherein the seal rings 166, 168 are relatively large in diameter.
  • a seal assembly using a channel configuration somewhat similar to that described above but without splined load rings and splined seal rings is described in commonly-owned PCT application no. PCT/US 98/17569, filed 25 August 1998.
  • a seal ring 66 having a splined configuration may be useful with a non-splined load ring, such as illustrated in the aforementioned 5,527,046 patent, to prevent rotation of the load ring relative to the seal ring 66.
  • a splined load ring 70 may be useful with a non-splined seal ring, such as illustrated in the 5,527,046 patent.
  • the seal assemblies 24, 26 described above are useful in increasing the life of the roller assembly 10 because a positive seal between the seal faces 74 can be maintained.
  • the interfitting relationship between the seal rings 66, 68 and the load ring 70, 72 resist rotation and slippage of the load rings 70, 72 relative to the seal rings 66, 68 even when the coefficient of friction between the seal faces 74 is greater than the coefficient of friction between one of the seal rings and the corresponding load ring. This is particularly true if the channels 300, 302 on the seal rings 66, 68 are utilized to provide additional resistance to slippage. Because the load rings 70, 72 resist slippage, there is less likelihood of seal failure.

Landscapes

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

Abstract

L'invention concerne un ensemble joint mécanique (24, 26) comprenant une paire de bagues (66, 68) d'étanchéité en vis-à-vis dont les faces (74) d'étanchéité coopèrent. Les faces (74) d'étanchéité sont maintenues au contact hermétique d'une paire de bagues (70, 72) de charge élastiques dont les surfaces annulaires (106) coopèrent avec les surfaces annulaires (72) opposées des bagues (66, 68) d'étanchéité. Les surfaces annulaires (102, 106) de contact de chacune des bagues (66, 68) d'étanchéité et leur bague (70, 72) de charge correspondante sont configurées de manière que leurs parties alignées coopèrent les unes avec les autres et empêchent ainsi toute rotation relative des bagues (70, 72). En particulier, chaque bague (70, 72) d'étanchéité possède des cannelures (100) périphériques espacées qui correspondent aux cannelures (104) périphériques espacées de la bague (70, 72) d'étanchéité correspondante. La bague (66, 68) d'étanchéité peut également être pourvue d'un canal (300, 302) périphérique ouvert dans lequel vient se loger une partie terminale de la bague (70, 72) de charge pour empêcher la rotation entre la bague (70, 72) de charge et la bague (66, 68) d'étanchéité.
PCT/US1998/026332 1997-12-12 1998-12-10 Ensemble joint mecanique a bagues de charge cooperant avec des bagues d'etancheite WO1999031411A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US6938697P 1997-12-12 1997-12-12
US60/069,386 1997-12-12

Publications (1)

Publication Number Publication Date
WO1999031411A1 true WO1999031411A1 (fr) 1999-06-24

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1998/026332 WO1999031411A1 (fr) 1997-12-12 1998-12-10 Ensemble joint mecanique a bagues de charge cooperant avec des bagues d'etancheite

Country Status (1)

Country Link
WO (1) WO1999031411A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2154750C1 (ru) * 1999-06-25 2000-08-20 Потребительское общество "Финэкс" Торцовое уплотнение центробежного насоса
DE19955860B4 (de) * 1999-11-20 2004-04-08 Federal-Mogul Burscheid Gmbh Gleitringdichtung
DE102011013366A1 (de) * 2011-03-08 2012-09-13 Federal-Mogul Burscheid Gmbh Gleitringdichtung
WO2020263454A1 (fr) 2019-06-25 2020-12-30 Caterpillar Inc. Joint d'étanchéité résistant au couple

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4183542A (en) * 1977-10-21 1980-01-15 Fonderia R. Bertoldo & C. S.a.s. Rotating face sealing gasket, particularly for use on tracked vehicles
US4421327A (en) * 1981-12-17 1983-12-20 Morley James P Heavy duty end face seal with asymmetrical cross-section
USH1180H (en) * 1991-12-23 1993-05-04 Caterpillar Inc. Face seal with increased torque transfer capacity
US5527046A (en) 1994-12-15 1996-06-18 Caterpillar Inc. Seal assembly having resilient load rings
US9817569B2 (en) 2010-12-29 2017-11-14 Microsoft Technology Licensing, Llc Virtual controller for touch display

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4183542A (en) * 1977-10-21 1980-01-15 Fonderia R. Bertoldo & C. S.a.s. Rotating face sealing gasket, particularly for use on tracked vehicles
US4421327A (en) * 1981-12-17 1983-12-20 Morley James P Heavy duty end face seal with asymmetrical cross-section
USH1180H (en) * 1991-12-23 1993-05-04 Caterpillar Inc. Face seal with increased torque transfer capacity
US5527046A (en) 1994-12-15 1996-06-18 Caterpillar Inc. Seal assembly having resilient load rings
US9817569B2 (en) 2010-12-29 2017-11-14 Microsoft Technology Licensing, Llc Virtual controller for touch display

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2154750C1 (ru) * 1999-06-25 2000-08-20 Потребительское общество "Финэкс" Торцовое уплотнение центробежного насоса
DE19955860B4 (de) * 1999-11-20 2004-04-08 Federal-Mogul Burscheid Gmbh Gleitringdichtung
DE102011013366A1 (de) * 2011-03-08 2012-09-13 Federal-Mogul Burscheid Gmbh Gleitringdichtung
DE102011013366B4 (de) * 2011-03-08 2014-10-02 Federal-Mogul Burscheid Gmbh Gleitringdichtung
US9404583B2 (en) 2011-03-08 2016-08-02 Federal-Mogul Burscheid Gmbh Slide ring seal
WO2020263454A1 (fr) 2019-06-25 2020-12-30 Caterpillar Inc. Joint d'étanchéité résistant au couple
CN114096769A (zh) * 2019-06-25 2022-02-25 卡特彼勒公司 抗扭矩密封件
KR20220024809A (ko) * 2019-06-25 2022-03-03 캐타필라 인코포레이티드 토크 저항성 씰
US11592111B2 (en) 2019-06-25 2023-02-28 Caterpillar Inc. Torque resistant seal
KR102704026B1 (ko) 2019-06-25 2024-09-09 캐타필라 인코포레이티드 토크 저항성 씰

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