WO2002093046A1 - Joint mecanique - Google Patents

Joint mecanique Download PDF

Info

Publication number
WO2002093046A1
WO2002093046A1 PCT/GB2002/002162 GB0202162W WO02093046A1 WO 2002093046 A1 WO2002093046 A1 WO 2002093046A1 GB 0202162 W GB0202162 W GB 0202162W WO 02093046 A1 WO02093046 A1 WO 02093046A1
Authority
WO
WIPO (PCT)
Prior art keywords
seal
seal face
textured
mechanical seal
face
Prior art date
Application number
PCT/GB2002/002162
Other languages
English (en)
Inventor
Alan Roddis
Original Assignee
Aes Engineering 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
Priority claimed from GB0111716A external-priority patent/GB0111716D0/en
Application filed by Aes Engineering Limited filed Critical Aes Engineering Limited
Publication of WO2002093046A1 publication Critical patent/WO2002093046A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
    • F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
    • F16J15/3424—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 microcavities
    • 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

Definitions

  • This invention relates to mechanical seals used to seal equipment with rotating components.
  • a mechanical seal comprises a "floating" component which is mounted so as to be axially movable around the rotary shaft of, for example, a pump and a “static” component which is axially fixed, typically being secured to a housing.
  • the floating component has a flat annular end face, i.e. its seal face, directed towards a complementary seal face of the static component.
  • the floating component is urged towards the static component to close the seal faces together to form a sliding face seal, usually by means of one or more spring members.
  • one of the floating and static components rotates; this component is referred to as the rotary component.
  • the other of the floating and static components does not rotate and is referred to as the stationary component.
  • the sliding interface between the rotary and stationary components is particularly important to the operational performance of the mechanical seal.
  • the varying conditions at the sliding interface between a pair of mechanical seal faces, are well documented.
  • the term "fluid film” is often used to describe the lubrication characteristics at the sliding interface. It is commonly understood that the action of a rotating component sliding against a stationary component can create undesirable operational conditions. Such conditions include the generation of heat, increased equipment power consumption, increased component wear and ultimately reduced component operational life.
  • An etched surface across the entire radial seal face width can, in some circumstances, lead to static seal face leakage. This is due to the respective distance between any two micropores and the hydrostatic effects of the fluid film under media pressure.
  • a mechanical seal to provide sealing between a rotatable shaft and a housing, the seal having a stationary part for connection to the housing and a rotary part for rotation with the shaft, mating sealing faces being carried by said stationary and rotary parts, said rotary parts being for mounting on the drive shaft for rotation therewith, at least one seal face having a textured portion and a non-textured portion, the non-textured portion acting as a sealing dam
  • edge of the sealing dam is positioned at or close to the seal face balance diameter.
  • the sealing dam may be radially positioned on the lower pressure side of the seal face relative to the textured portion.
  • the sealing dam may be radially positioned on the higher pressure side of the seal face relative to the textured portion.
  • the sealing dam may cover up to 99 per cent of the seal face area and correspondingly the textured surface may cover up to 99 per cent of the seal face area.
  • the textured surface consists of micropores or indentations in the surface of the seal face.
  • micropores or indentations may be evenly distributed in the area of the seal face adjacent to the sealing dam. Alternatively they may be randomly distributed in the area of the seal face adjacent to the sealing dam.
  • Figure 1 illustrates an end view of a prior art seal face design extracted from US 6,046,430 (Etsion).
  • Figure 2 is a graph which compares the typical start up torque required to overcome the ringing or sticking effect of a conventional "non-textured" seal face to that of a micropore “textured” seal face which is textured across its entire radial length, over a range of process pressures using water as a process media.
  • Figure 3 is a graph which corresponds to Figure 2 but uses a nitrogen gas as the process media.
  • Figure 4 is a partial longitudinal cross section through a single cartridge mechanical seal of the invention.
  • Figure 5 is a sectional view showing the invention and corresponding to
  • Figure 6 is a partial longitudinal cross section through a double cartridge mechanical seal of the invention.
  • Figure 7 is a cross section through a seal face showing a sealing dam and typical micropore indentations in its surface.
  • Figure 8a is an end view of a seal face with a surface texture across its entire radial cross section.
  • Figure 8b corresponds to Figure 8a and part of Figure 6 and is an end view of a seal face of the invention with a portion of its seal face encompassing a sealing dam and a surface textured portion.
  • Figure 1 shows a prior art arrangement as previously mentioned.
  • Figure 3 clearly shows a similar torque difference between a fully textured seal face and a conventional seal face when starting a mechanical seal operating in nitrogen gas.
  • the rotary and axially floating seal face (1) is spring biased towards a static stationary seal face (2).
  • the rotary seal face (1) is allowed to slide on the static seal face (2).
  • the interface between the rotary seal face (1) and stationary seal face (2) forms sealing area (3).
  • This sealing area (3) is the primary seal that prevents the process media (4) from escaping from the process chamber (5).
  • the process media (4) is sealed by a sleeve elastomer (6) in contact with the shaft (7) and sleeve (8). This has been termed the first secondary sealing area (9).
  • the second secondary sealing area (10) is formed between stationary seal face (2) and stationary gland (11) using elastomer (12).
  • the third secondary sealing area (13) is formed between the rotary seal face (1) and the sleeve (8) using elastomer (14).
  • the fourth secondary sealing area (15) is formed between the gland (11) and the process chamber (5) using gasket (16).
  • At least one of the two sealing faces, rotary (1) and stationary (2) has a partly micropore textured surface (17).
  • Said micropore textured surface, in single seal operation, preferably extends radially inwardly from the outside diameter terminating at the sealing dam.
  • the invention illustrated in Figure 4 therefore offers a cartridge mechanical seal with at least one set of mechanical seal faces which are textured across only part of the radial cross section.
  • Figure 5 shows the section at the mechanical seal faces which corresponds to Figure 4.
  • Figure 5 illustrates an inwardly positioned sealing dam (18) since the micropore textured surface (17) is positioned radially outwardly to the sealing dam (18).
  • This seal dam (18) invention provides an adequate, non- textured sealing surface for static applications.
  • the sealing dam (18) It is considered advantageous to locate the edge of the sealing dam (18) at or close to the seal balance diameter (19). It is further advantageous, although not essential, for the radially largest part of the sealing dam (18) to coincide with the mechanical seal face balance line (19). The sealing dam (18) therefore protrudes radially inwardly allowing the micropore surface (17) to be lubricated by the process fluid (4). From the single seal design in Figure 4, the process fluid (4) is often at a higher pressure than the inner most part of the seal face (3). This radially inner most part of a single seal design is often termed the atmospheric side of the seal face (3).
  • the sealing dam to balance diameter ratio can be changed to suit specific applications. Likewise the percentage seal face area coverage of the sealing dam and textured surface can be changed to create optimised conditions at the fluid film, for given process conditions.
  • the radially smallest part of the sealing dam (18) can be designed to coincide with the mechanical seal face balance diameter (19).
  • the sealing dam (18) therefore protrudes radially outwardly allowing the micropore surface (17) adjacent to the lower pressure or atmospheric side of the seal faces (3). This is shown in Figure 6, assuming the barrier pressure (20) is lower than the process pressure (4).
  • Hydrostatic fluid film conditions between the mechanical seal faces (3) are a known and well-documented fact of mechanical seal design.
  • the hydrostatic fluid film conditions between any two mating seal faces (3) may be approximated as a linear pressure drop.
  • the linear pressure drop creates an axially thicker fluid film at the higher pressure outer or inner most radial side of the seal faces (3).
  • the fluid film then reduces in a linear axially manner to the radially lower pressure side of the seal faces (3). At the lower pressure side of the seal faces the fluid film is said to be "thin".
  • Figure 6 illustrates the invention applied to a double cartridge mechanical seal. From Figure 6 the stationary and axially floating seal face (2) is spring biased towards an axially static rotary seal face (1). The rotary face (1) is allowed to slide on the stationary seal face (2). The interface between the rotary seal face (1) and stationary seal face (2) forms sealing area (3). This sealing area (3) is the primary seal that prevents the process media (4) from escaping from the process chamber (5).
  • the second primary seal is made in the barrier media chamber (20) on the outboard side of the mechanical seal.
  • the stationary and axially floating seal face (21) is spring biased towards an axially static rotary seal face (22).
  • the rotary face (22) is allowed to slide on the stationary seal face (21).
  • the interface between the rotary seal face (22) and stationary seal face (21) forms sealing area (23).
  • This sealing area (23) is the primary seal that prevents the barrier media from escaping from the barrier media chamber (20).
  • the sealing dam (24) is positioned approximately radially outwardly of the seal face balance diameter (25), whilst the textured surface (26) is positioned adjacent to the barrier media in the barrier media chamber (20).
  • Figure 7 shows a cross section through a seal face of the invention.
  • the micropore indentations (27) have been shown as spherical indentations which penetrate the surface in depth up to, but preferably less than, the radius of the spherical indentation. It is considered self evident that the surface indentations could be of any physical shape, but ideally be of a symmetrical nature (viewed on the end of the seal face) and of any physical depth.
  • the seal face comprises of a sealing dam portion (24) and a textured portion (26)
  • the spacing of the micropore indentations (27) has minimal influence on the static sealability of the seal face. It is therefore possible to distribute the micropore indentations (27) so that they are positioned as close to each other as physically possible.
  • the micropore indentations (27) could cover up to 95% of the designated textured surface area (26).
  • This invention therefore allows the optimum dynamic performance of the mechanical seal without increasing the physical radial cross section (28) of the seal face. This reduces heat generation, power consumption and seal face wear in comparison to a conventional mechanical seal.
  • the mean ringing force may be approximated to lie on the radius midway between the outside radius (Rmax) of the seal face and inside radius (Rmin) of the seal face.
  • This is mean radius (Rmean) is shown in Figure 8a.
  • Figure 8b shows the mean radius (Rmean), where the ringing force acts, on a seal face of the invention when the micropore surface (17) is on the radially most inner part of the seal face (3). Comparing Figures 8a and 8b, for the same seal face radial cross section, the mean radius is smaller in that of the invention ( Figure 8b).
  • Torque is derived from Force and Radius. If we assume the same amount of surface indentations in the two designs, the force will be constant. If the mean radius of the invention reduces, then the torque required to overcome the ringing effect in the invention will be proportionally smaller.
  • This reduction in torque, of the invention is significant, and reduces the likelihood of damaging the seal face in equipment start up conditions.
  • the invention may be employed for at least one seal face, for both rotary seals and stationary seals, single, double or triple mechanical seals, whether designed in a cartridge or component seal format. It is also considered self evident that the invention may be used with metallic components as well as non-metallic components. Some types of equipment rotate the housing and have a stationary shaft. It is considered that the invention can be similarly applied to such designs.
  • the invention may be employed for seal designs with hydraulically balanced seal faces as well as hydraulically unbalanced seal faces.
  • the textured micropore portion of the seal face may differ between each set of faces.
  • the micropore portion may be on the inner radial portion of at least one seal face in contact with the process media (4) and on the outer radial portion of at least one seal face in contact with the barrier media (20).

Landscapes

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

Abstract

L'invention concerne un joint mécanique, assurant l'étanchéité entre un arbre rotatif et un carter. Le joint mécanique comporte d'une face d'étanchéité (3) munie d'une partie texturée (17) et d'une partie non texturée (18). La partie non texturée agit comme une barrière d'étanchéité.
PCT/GB2002/002162 2001-05-15 2002-05-15 Joint mecanique WO2002093046A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GB0111716A GB0111716D0 (en) 2001-05-15 2001-05-15 A mechanical seal with a textured seal face
GB0111716.7 2001-05-15
GB0200147A GB0200147D0 (en) 2001-05-15 2002-01-02 A mechanical seal with a textured seal face
GB0200147.7 2002-01-02

Publications (1)

Publication Number Publication Date
WO2002093046A1 true WO2002093046A1 (fr) 2002-11-21

Family

ID=26246072

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2002/002162 WO2002093046A1 (fr) 2001-05-15 2002-05-15 Joint mecanique

Country Status (1)

Country Link
WO (1) WO2002093046A1 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006070205A1 (fr) * 2004-12-30 2006-07-06 Aes Engineering Limited Joint rotatif
CN103470762A (zh) * 2013-08-20 2013-12-25 浙江工业大学 倾斜渐变多孔端面非接触式机械密封结构
CN104154235A (zh) * 2014-05-07 2014-11-19 清华大学 螺旋分布收敛型微孔织构机械密封
WO2015031474A1 (fr) * 2013-08-27 2015-03-05 Eaton Corporation Composite pour bague d'étanchéité permettant une meilleure étanchéité hydrodynamique
WO2015041048A1 (fr) * 2013-09-18 2015-03-26 イーグル工業株式会社 Composant coulissant
US9714712B2 (en) 2014-08-15 2017-07-25 Eaton Corporation Hydrodynamic mating ring with integrated groove inlet pressure control
US9970478B2 (en) 2013-09-18 2018-05-15 Eagle Industry Co., Ltd. Sliding parts
EP3627011A4 (fr) * 2017-05-19 2021-01-20 Eagle Industry Co., Ltd. Composant coulissant
US11035411B2 (en) 2017-07-14 2021-06-15 Eagle Industry Co., Ltd. Sliding parts
US11125334B2 (en) 2016-12-21 2021-09-21 Eaton Intelligent Power Limited Hydrodynamic sealing component and assembly
US11248707B2 (en) 2017-05-19 2022-02-15 Eagle Industry Co., Ltd Sliding component
US11708911B2 (en) 2017-10-03 2023-07-25 Eagle Industry Co., Ltd. Sliding component

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4925490A (en) * 1987-12-28 1990-05-15 Tanken Seiko Kabushiki Kaisha Mechanical seal using pore-dispersed material, and pore-dispersed cemented carbide and method for manufacturing same
EP0466076A2 (fr) * 1990-07-09 1992-01-15 Ebara Corporation Garniture à bague glissante avec rainures hélicoidales
EP0470409A1 (fr) * 1990-07-18 1992-02-12 Ebara Corporation Garniture mécanique d'étanchéité sans contact
US5092612A (en) * 1986-10-28 1992-03-03 Pacific Wietz Gmbh & Co. Kg Contactless pressurizing-gas shaft seal
US5435574A (en) * 1986-10-28 1995-07-25 Pacific Wietz Gmbh & Co. Kg Contactless pressurizing-gas shaft seal
US5664787A (en) * 1994-03-22 1997-09-09 Nippon Pillar Packing Co., Ltd. Non-contacting shaft sealing device
EP0935086A2 (fr) * 1998-02-06 1999-08-11 John Crane Inc. Garniture d'étanchéité lubrifiée au gaz pour faibles vitesses de rotation
US6046430A (en) * 1996-09-30 2000-04-04 Surface Technologies Ltd. Bearing having micropores, and design method therefor
US6341782B1 (en) * 2000-03-03 2002-01-29 Surface Technologies Ltd Lubricated seals having micropores

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5092612A (en) * 1986-10-28 1992-03-03 Pacific Wietz Gmbh & Co. Kg Contactless pressurizing-gas shaft seal
US5435574A (en) * 1986-10-28 1995-07-25 Pacific Wietz Gmbh & Co. Kg Contactless pressurizing-gas shaft seal
US4925490A (en) * 1987-12-28 1990-05-15 Tanken Seiko Kabushiki Kaisha Mechanical seal using pore-dispersed material, and pore-dispersed cemented carbide and method for manufacturing same
EP0466076A2 (fr) * 1990-07-09 1992-01-15 Ebara Corporation Garniture à bague glissante avec rainures hélicoidales
EP0470409A1 (fr) * 1990-07-18 1992-02-12 Ebara Corporation Garniture mécanique d'étanchéité sans contact
US5664787A (en) * 1994-03-22 1997-09-09 Nippon Pillar Packing Co., Ltd. Non-contacting shaft sealing device
US6046430A (en) * 1996-09-30 2000-04-04 Surface Technologies Ltd. Bearing having micropores, and design method therefor
EP0935086A2 (fr) * 1998-02-06 1999-08-11 John Crane Inc. Garniture d'étanchéité lubrifiée au gaz pour faibles vitesses de rotation
US6341782B1 (en) * 2000-03-03 2002-01-29 Surface Technologies Ltd Lubricated seals having micropores

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
ETSION I ET AL: "A MODEL FOR MECHANICAL SEALS WITH REGULAR MICROSURFACE STRUCTURE", TRIBOLOGY TRANSACTIONS, THE SOCIETY, PARK RIDGE, IL,, US, vol. 3, no. 39, July 1996 (1996-07-01), pages 677 - 683, XP001094562, ISSN: 1040-2004 *

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006070205A1 (fr) * 2004-12-30 2006-07-06 Aes Engineering Limited Joint rotatif
GB2436778A (en) * 2004-12-30 2007-10-03 Aes Eng Ltd Rotary seal
GB2436778B (en) * 2004-12-30 2009-06-03 Aes Eng Ltd Rotary seal
CN103470762A (zh) * 2013-08-20 2013-12-25 浙江工业大学 倾斜渐变多孔端面非接触式机械密封结构
US10337619B2 (en) 2013-08-27 2019-07-02 Eaton Intelligent Power Limited Seal ring composite for improved hydrodynamic seal performance
WO2015031474A1 (fr) * 2013-08-27 2015-03-05 Eaton Corporation Composite pour bague d'étanchéité permettant une meilleure étanchéité hydrodynamique
CN107269705A (zh) * 2013-09-18 2017-10-20 伊格尔工业股份有限公司 滑动部件
US9970478B2 (en) 2013-09-18 2018-05-15 Eagle Industry Co., Ltd. Sliding parts
EP3284982B1 (fr) * 2013-09-18 2024-03-20 Eagle Industry Co., Ltd. Composant coulissant
JP2017166701A (ja) * 2013-09-18 2017-09-21 イーグル工業株式会社 しゅう動部品
WO2015041048A1 (fr) * 2013-09-18 2015-03-26 イーグル工業株式会社 Composant coulissant
US9829043B2 (en) 2013-09-18 2017-11-28 Eagle Industry Co., Ltd. Sliding parts
US9915289B2 (en) 2013-09-18 2018-03-13 Eagle Industry Co., Ltd. Sliding parts
JPWO2015041048A1 (ja) * 2013-09-18 2017-03-02 イーグル工業株式会社 しゅう動部品
CN104154235A (zh) * 2014-05-07 2014-11-19 清华大学 螺旋分布收敛型微孔织构机械密封
US9714712B2 (en) 2014-08-15 2017-07-25 Eaton Corporation Hydrodynamic mating ring with integrated groove inlet pressure control
US11125334B2 (en) 2016-12-21 2021-09-21 Eaton Intelligent Power Limited Hydrodynamic sealing component and assembly
EP3627011A4 (fr) * 2017-05-19 2021-01-20 Eagle Industry Co., Ltd. Composant coulissant
US11053975B2 (en) 2017-05-19 2021-07-06 Eagle Industry Co., Ltd Sliding component
US11248707B2 (en) 2017-05-19 2022-02-15 Eagle Industry Co., Ltd Sliding component
US11035411B2 (en) 2017-07-14 2021-06-15 Eagle Industry Co., Ltd. Sliding parts
US11708911B2 (en) 2017-10-03 2023-07-25 Eagle Industry Co., Ltd. Sliding component

Similar Documents

Publication Publication Date Title
JP6861730B2 (ja) しゅう動部品
US6325380B1 (en) Face seal assembly
US7377518B2 (en) Mechanical seal ring assembly with hydrodynamic pumping mechanism
US5201531A (en) Face seal with double spiral grooves
US8074995B2 (en) Low and reverse pressure application hydrodynamic pressurizing seals
US5169159A (en) Effective sealing device for engine flowpath
EP0595437B1 (fr) Garniture mécanique d'étanchéité
US6655693B2 (en) Non-contacting gas compressor seal
EP0013678B1 (fr) Joint d'étanchéité mécanique muni de gorges en spirale, à auto-rétablissement de la position relative
EP0163450B1 (fr) Garniture d'étanchéité à anneau glissant
US5516118A (en) Circumferential hydrodynamic seals for sealing a bidirectionally rotatable member
EP3315832B1 (fr) Élément de glissement
EP0568192A1 (fr) Joint secondaire pour turbine à gaz
EP0375686A1 (fr) Joint mecanique a anneaux glissants pourvu d'un organe de centrage.
CA2453877A1 (fr) Raccord union a refroidissement de fluide
WO2002093046A1 (fr) Joint mecanique
AU2009232214B2 (en) Internally pressurised seals
CA2210609C (fr) Joint d'etancheite a soufflet a capacite de fonctionnement en pression inverse
US5192083A (en) Single ring sector seal
US5531458A (en) Face seal with angled grooves
US5006043A (en) Floating annular seal with thermal compensation
CN108413040A (zh) 唇形机械密封装置
CN208364788U (zh) 唇形机械密封装置
US10036474B2 (en) Vented lift off seal assemblies
JP2577417Y2 (ja) メカニカルシール

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NO NZ OM PH PL PT RO RU SD SE SG SI SK SL TJ TM TN TR TT TZ UA UG US UZ VN YU ZA ZM ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): GH GM KE LS MW MZ SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

121 Ep: the epo has been informed by wipo that ep was designated in this application
REG Reference to national code

Ref country code: DE

Ref legal event code: 8642

122 Ep: pct application non-entry in european phase
NENP Non-entry into the national phase

Ref country code: JP

WWW Wipo information: withdrawn in national office

Country of ref document: JP