WO2004053365A1 - Assemblage joint - Google Patents

Assemblage joint Download PDF

Info

Publication number
WO2004053365A1
WO2004053365A1 PCT/GB2003/005276 GB0305276W WO2004053365A1 WO 2004053365 A1 WO2004053365 A1 WO 2004053365A1 GB 0305276 W GB0305276 W GB 0305276W WO 2004053365 A1 WO2004053365 A1 WO 2004053365A1
Authority
WO
WIPO (PCT)
Prior art keywords
seal
assembly
seal body
axis
housing
Prior art date
Application number
PCT/GB2003/005276
Other languages
English (en)
Inventor
Peter Francis Crudgington
Original Assignee
Cross Manufacturing Company (1938) Limited
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 Cross Manufacturing Company (1938) Limited filed Critical Cross Manufacturing Company (1938) Limited
Priority to AU2003285585A priority Critical patent/AU2003285585A1/en
Publication of WO2004053365A1 publication Critical patent/WO2004053365A1/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
    • F16J15/44—Free-space packings
    • F16J15/441—Free-space packings with floating ring
    • F16J15/442—Free-space packings with floating ring segmented

Definitions

  • This invention relates to seal assemblies for sealing between a stator and an element rotating about an axis.
  • US-A-5026252 shows a hybrid arrangement, which attempts to combine the features of bristle seals and shoe seals, but the result is to introduce a potential leakage path between the bristle ends and the shoe and it is difficult to ensure uniform bristle distortion as a result of radial movements of the shoe. Further the location of the shoe relies entirely on the weld to the very thin bristles and circumferential movement is also not well addressed.
  • the present invention consists in a seal assembly for sealing between a stator and an element rotating about an axis within the stator to separate a higher pressure region from a lower pressure region, the assembly including a housing for disposal circumjacent the rotating element and defining a radially opening channel facing the axis, a seal body having a first portion slidably received in the channel for inward and outward movement therein and a second portion having a surface for forming a seal at an interface with the rotating element and at least one resilient element for urging the seal body towards the axis to form the seal wherein the resilient element restricts or prevents circumferential movement of the seal body relative to the axis.
  • seal bodies or shoes arranged circumferentially side-by-side in the channel to abut end to end.
  • the abutting ends of the respective pairs of seal bodies may form a labyrinth seal and additionally or alternatively a member or members may be provided for extending across the joint between the seal body abutting ends.
  • the resilient element is a leaf spring and, for example, the leaf spring may extend generally circumferentially between the housing and the seal body.
  • the leaf spring may be cranked and the relative lengths of the portions of the leaf spring either side of the crank may be selected so that only radial movement relative to the axis can occur.
  • the second portion of the seal body may be axially wider than the first portion to provide an extension for lying in the lower pressure region.
  • the seal surface may be profiled for forming a hydrodynamic film or films between the seal surface and the rotating element or, alternatively it may have one or more cavities for connection to a high pressure source to form a hydrostatic bearing.
  • the seal body may include one or more conduits extending between the cavities and a face of the seal body, which is exposed to the higher pressure region in use.
  • the seal body may be made from a plurality of parts and the seal surface may be constituted by different material from the bulk of the seal body. Thus it may be formed by a trim attached to the main part of the seal body, for example by rivets, or it may be formed by a coating.
  • the invention further includes a rotary machine including a stator, a rotatable element and seal assembly as set out above.
  • the seal body may be dimensioned such that the integral of the pressure drop across the seal assembly on the housing or stator size is at least approximately equal to the integral of equivalent pressure drop across the seal side.
  • Figure 1 is a schematic vertical section through a seal disposed in relation to a rotating shaft or disc;
  • Figure 2 is a vertical section through Figure 1 on the line ll-ll;
  • Figure 3a illustrates the seal surface of the seal illustrated in Figure 1 in an embodiment which forms hydrodynamic films
  • Figure b illustrates an embodiment which forms a hydrostatic bearing
  • Figures 4a to c are schematic illustrations of abutting joints formed between seal bodies
  • Figures 5a and b respectively show an integral seal body and a multi- component seal body
  • Figure 6 illustrates the pressure drops across either side of the seal body
  • FIGS. 7a to c illustrate different spring constructions for use in the invention
  • Figure 8 illustrates a particular embodiment of the Figure 7a proposal
  • Figure 9 illustrates an alternative construction of the Figure 7c proposal
  • Figure 10 illustrates a further embodiment of the seal assembly
  • Figure 11 illustrates a modification of the seal assembly
  • Figure 12 illustrates a further modification of the seal assembly
  • Figure 13 illustrates the pressure drops across either side of the seal body of Figure 11.
  • a seal assembly is shown in relation to a rotor or disc 11 , which is rotating about an axis 12.
  • the seal assembly comprises a housing generally indicated at 13 and a seal body or shoe 14.
  • the housing 13 and seal body 14 are interconnected by springs 15.
  • the shoe 14 has a first portion 16, which is slidingly received in a channel 17 defined by the housing 13 for radial movement relative to the rotor or disc 11.
  • the springs 15 act in a sense to urge the seal body 14 against the peripheral surface of the rotor or disc 11.
  • the shoe 14 includes a second portion, which defines a sealing surface 18 that forms the seal at the interface with the rotor or disc 11. As can be seen the second portion can include an extension or plough 19 for increasing the size of the seal surface 18.
  • the springs 15 comprise leaf springs extending between the housing 13 and a circumferentially spaced point on the shoe or seal body 14. In the particular embodiment these springs are in line. It will be understood that the springs are relatively resilient in the radial direction allowing for self adjustment in the shoe position so that the seal can be formed as will be discussed in more detail below, but are relatively stiff in the circumferential direction so that little or no circumferential movement of the shoe can take place. This means that the designed gaps 21 between adjacent shoes
  • Figure 3a illustrates the use of cavities 22 to form hydrodynamic pads, in a known manner.
  • the seal surface 18 may simply be slightly frustoconical in shape so as to form a hydrodynamic film.
  • Figure 3b cavities 23 are connected to the high pressure side of the seal assembly by conduits 24 allowing a hydrostatic bearing to be formed.
  • FIGS. 4a to c illustrate various possible abutments between the ends
  • Figure 5a the seal body or shoe 14 is illustrated.
  • the seal body or shoe 14 is an integral element, whereas in Figure 5b the sealing surface 18 is carried on another element 25, which may be a layer of material riveted to the main body of 14 or may simply be a coating.
  • Figure 6 illustrates the pressure profile on the inner and outer sides of the seal body 14. It will be seen that by suitable choice of the dimensions L a and U so that the integrals of the pressure curves on either side are equal.
  • Figures 7a to c illustrate different spring arrangements. In Figure 7a compression springs 26 are used instead of the leaf springs 15 and these sit in aligned pairs of recesses in the housing 13 and the shoe or seal body 14 respectively. This combination of springs again restricts circumferential movement, without introducing significant friction in the radial direction.
  • Figure 7c is essentially the Figure 1 embodiment, whilst Figure 7c introduces a development of that concept, where the springs 15 are cranked at 27.
  • crank springs 15 are shown as being cut out as an integral part of the shoe and then they may be welded, riveted or otherwise attached, for example as illustrated in Figure 9.
  • shims 28 are mounted to extend across the gaps 22, enhancing the effectiveness of the seal. These shims or thin shoes 28 are mounted by their leaf springs onto the main seal mounting.
  • Figure 11 shows a modification of the design in which the shoe 14 is made axially shorter.
  • the pressure above the shoe 14 has been reduced to an intermediate pressure Pint.
  • This intermediate pressure has been achieved by placing holes 30 and 31 in the front and back plate, respectively, of the shoe 14.
  • the holes 31 are sized larger than the holes 30.
  • the relationship between the hole sizes is governed by the theory of compressible flow and is highly dependant on the overall pressure ratio across the seal.
  • Figure 12 shows a seal working on a similar principle to the arrangement of Figure 11 , but in this case several radial slots are formed in the shoe 14 to control the pressure above the shoe.
  • Slot 32 in the front plate of the shoe 14 is narrower than slot 33 in the back plate of the shoe so as to create a reduced pressure Pint as in the seal of Figure 11.
  • the relationship of the slot widths/areas is governed by compressible flow theory.

Landscapes

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

Abstract

L'invention concerne un assemblage joint (10) servant à obturer un espace entre un stator et un élément (11) tournant autour d'un axe (12) à l'intérieur du stator, afin de séparer une zone de haute pression d'une zone de basse pression. L'assemblage comprend un boîtier (13) pour loger de façon circonvoisine l'élément rotatif et délimiter un canal à ouverture radiale (17) faisant face à l'axe. L'assemblage comprend également un corps de joint (14) présentant une première partie (16) disposée de manière coulissante dans le canal pour s'y déplacer en avant et en arrière, et une seconde partie présentant une surface (18) servant à former un joint au niveau d'une interface avec l'élément rotatif. L'assemblage comprend en outre au moins un élément souple (15) qui force le corps de joint à se déplacer vers l'extérieur pour former le joint. L'élément souple limite ou empêche un mouvement circonférentiel du corps de joint relativement à l'axe.
PCT/GB2003/005276 2002-12-07 2003-12-04 Assemblage joint WO2004053365A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003285585A AU2003285585A1 (en) 2002-12-07 2003-12-04 Seal assembly

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0228586A GB0228586D0 (en) 2002-12-07 2002-12-07 Seal assembly
GB0228586.4 2002-12-07

Publications (1)

Publication Number Publication Date
WO2004053365A1 true WO2004053365A1 (fr) 2004-06-24

Family

ID=9949268

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2003/005276 WO2004053365A1 (fr) 2002-12-07 2003-12-04 Assemblage joint

Country Status (3)

Country Link
AU (1) AU2003285585A1 (fr)
GB (1) GB0228586D0 (fr)
WO (1) WO2004053365A1 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1674771A1 (fr) * 2004-12-23 2006-06-28 Siemens Aktiengesellschaft Dispositif d'étanchéité entre un premier et un second élément
EP2048366A1 (fr) 2007-10-09 2009-04-15 Siemens Aktiengesellschaft Turbomachine avec segment de joint à labyrinthe ayant un rappel élastique
WO2010076641A1 (fr) * 2008-12-31 2010-07-08 Eaton Corporation Joint inter-arbre hydrodynamique et ensemble
EP2213842A1 (fr) * 2009-01-29 2010-08-04 Siemens Aktiengesellschaft Ensemble hydrostatique de joint d'étanchéité d'une turbine à vapeur
US9714712B2 (en) 2014-08-15 2017-07-25 Eaton Corporation Hydrodynamic mating ring with integrated groove inlet pressure control
EP3318785A1 (fr) * 2016-11-02 2018-05-09 United Technologies Corporation Joint annulaire segmenté
EP3492705A1 (fr) * 2017-12-01 2019-06-05 General Electric Technology GmbH Système d'étanchéité à film fluide
US10337619B2 (en) 2013-08-27 2019-07-02 Eaton Intelligent Power Limited Seal ring composite for improved hydrodynamic seal performance
WO2020050837A1 (fr) * 2018-09-05 2020-03-12 Siemens Aktiengesellschaft Joint d'étanchéité sans contact à ajustement mécanique
WO2020050835A1 (fr) * 2018-09-05 2020-03-12 Siemens Aktiengesellschaft Joint d'étanchéité sans contact à ajustement mécanique
US11125334B2 (en) 2016-12-21 2021-09-21 Eaton Intelligent Power Limited Hydrodynamic sealing component and assembly
US11635146B2 (en) 2021-07-27 2023-04-25 Stein Seal Company Circumferential sealing assembly with duct-fed hydrodynamic grooves

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2646475A1 (de) * 1976-05-26 1977-12-15 Philip Charles Stein Dichtung zum abdichten zwischen einem rotierenden element und einem gehaeuse
US5145189A (en) * 1991-09-11 1992-09-08 General Electric Company Hydro-lift dynamic circumferential seal
US5509664A (en) * 1993-07-19 1996-04-23 Stein Seal Company Segmented hydrodynamic seals for sealing a rotatable shaft
EP0995933A2 (fr) * 1998-10-19 2000-04-26 Stein Seal Company Joint hydro-dynamique d'étanchéité pour fluides compressibles
US6338490B1 (en) * 1998-08-05 2002-01-15 Societe Nationale d'Etude et de Construction de Moteurs d'Aviation “SNECMA” Sealing arrangement with automatic clearance adjustment

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2646475A1 (de) * 1976-05-26 1977-12-15 Philip Charles Stein Dichtung zum abdichten zwischen einem rotierenden element und einem gehaeuse
US5145189A (en) * 1991-09-11 1992-09-08 General Electric Company Hydro-lift dynamic circumferential seal
US5509664A (en) * 1993-07-19 1996-04-23 Stein Seal Company Segmented hydrodynamic seals for sealing a rotatable shaft
US6338490B1 (en) * 1998-08-05 2002-01-15 Societe Nationale d'Etude et de Construction de Moteurs d'Aviation “SNECMA” Sealing arrangement with automatic clearance adjustment
EP0995933A2 (fr) * 1998-10-19 2000-04-26 Stein Seal Company Joint hydro-dynamique d'étanchéité pour fluides compressibles

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1674771A1 (fr) * 2004-12-23 2006-06-28 Siemens Aktiengesellschaft Dispositif d'étanchéité entre un premier et un second élément
WO2006069817A1 (fr) * 2004-12-23 2006-07-06 Siemens Aktiengesellschaft Dispositif pour etancheifier un espace entre un premier et un deuxieme composant
US7997858B2 (en) 2004-12-23 2011-08-16 Siemens Aktiengesellschaft Arrangement for sealing off a gap between a first component and a second component
EP2048366A1 (fr) 2007-10-09 2009-04-15 Siemens Aktiengesellschaft Turbomachine avec segment de joint à labyrinthe ayant un rappel élastique
WO2010076641A1 (fr) * 2008-12-31 2010-07-08 Eaton Corporation Joint inter-arbre hydrodynamique et ensemble
US8100403B2 (en) 2008-12-31 2012-01-24 Eaton Corporation Hydrodynamic intershaft seal and assembly
EP2213842A1 (fr) * 2009-01-29 2010-08-04 Siemens Aktiengesellschaft Ensemble hydrostatique de joint d'étanchéité d'une turbine à vapeur
US10337619B2 (en) 2013-08-27 2019-07-02 Eaton Intelligent Power Limited Seal ring composite for improved hydrodynamic seal performance
US9714712B2 (en) 2014-08-15 2017-07-25 Eaton Corporation Hydrodynamic mating ring with integrated groove inlet pressure control
EP3318785A1 (fr) * 2016-11-02 2018-05-09 United Technologies Corporation Joint annulaire segmenté
US10082039B2 (en) 2016-11-02 2018-09-25 United Technologies Corporation Segmented annular seal
US11125334B2 (en) 2016-12-21 2021-09-21 Eaton Intelligent Power Limited Hydrodynamic sealing component and assembly
EP3492705A1 (fr) * 2017-12-01 2019-06-05 General Electric Technology GmbH Système d'étanchéité à film fluide
WO2019106024A1 (fr) * 2017-12-01 2019-06-06 General Electric Technology Gmbh Système d'étanchéité sans contact
WO2020050837A1 (fr) * 2018-09-05 2020-03-12 Siemens Aktiengesellschaft Joint d'étanchéité sans contact à ajustement mécanique
WO2020050835A1 (fr) * 2018-09-05 2020-03-12 Siemens Aktiengesellschaft Joint d'étanchéité sans contact à ajustement mécanique
US11635146B2 (en) 2021-07-27 2023-04-25 Stein Seal Company Circumferential sealing assembly with duct-fed hydrodynamic grooves

Also Published As

Publication number Publication date
GB0228586D0 (en) 2003-01-15
AU2003285585A1 (en) 2004-06-30

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