EP3112661A1 - Dispositif de scellement - Google Patents

Dispositif de scellement Download PDF

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Publication number
EP3112661A1
EP3112661A1 EP16176510.2A EP16176510A EP3112661A1 EP 3112661 A1 EP3112661 A1 EP 3112661A1 EP 16176510 A EP16176510 A EP 16176510A EP 3112661 A1 EP3112661 A1 EP 3112661A1
Authority
EP
European Patent Office
Prior art keywords
ring
shaft
bore
actuator assembly
closing member
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.)
Withdrawn
Application number
EP16176510.2A
Other languages
German (de)
English (en)
Inventor
Michael P. Cooke
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.)
Delphi International Operations Luxembourg SARL
Original Assignee
Delphi International Operations Luxembourg SARL
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 Delphi International Operations Luxembourg SARL filed Critical Delphi International Operations Luxembourg SARL
Publication of EP3112661A1 publication Critical patent/EP3112661A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/004—Joints; Sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0057—Means for avoiding fuel contact with valve actuator, e.g. isolating actuators by using bellows or diaphragms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/26—Fuel-injection apparatus with elastically deformable elements other than coil springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/707—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for avoiding fuel contact with actuators, e.g. isolating actuators by using bellows or diaphragms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8053—Fuel injection apparatus manufacture, repair or assembly involving mechanical deformation of the apparatus or parts thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/85—Mounting of fuel injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/85—Mounting of fuel injection apparatus
    • F02M2200/858—Mounting of fuel injection apparatus sealing arrangements between injector and engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/90—Selection of particular materials
    • F02M2200/9015—Elastomeric or plastic materials

Definitions

  • the present invention relates to a sealing arrangement particularly used in a servo injector.
  • a metal diaphragm or bellows is used when a force and/or motion needs to be transmitted between different fluids without the fluids mixing and without causing frictional forces.
  • Examples include Pressure transducers as disclosed in EP2759607 , valves as in EP2807411 and piezo-electric actuators described in EP1431569 .
  • a problem with such devices is that they are relatively expensive and it can require a lot of space to achieve sufficient movement without being over-stressed or generating excessive forces. It is well known to use an O-ring as a fluid seal, but these are known to have high friction and fluid seepage when they are sliding.
  • the sealing arrangement is adapted to force the O-ring to roll on the shaft and on the bore when the shaft translates relative to the bore so that sliding of the O-ring is avoided and sealing is ensured.
  • the shaft is provided with an annular groove in which is placed the O-ring, said O-ring rolling, in use, between the two edges of the groove so that when the shaft ends a longitudinal translation the annular passage restricts and the O-ring gets further compressed.
  • the bore is provided with a narrowing portion arranged at a first end of the portion of the bore so that under the influence of fuel pressure peaks the O-ring further deforms and further compresses in said narrowing portion.
  • the bore may be provided with a second narrowing portion arranged at a second end of the portion of the bore.
  • the invention also extend to an actuator assembly of a fuel injector, the actuator assembly extending along the longitudinal axis, an end of said actuator assembly being provided with a shaft member extending through a bore, the annular passage between the shaft and the bore being sealed by an O-ring, the shaft, the bore and the O-ring defining a sealing arrangement as described above.
  • the actuator assembly may further comprise a cylindrical sleeve closed at an extremity by a closing member having a wall defining the bore through which extends the shaft; said wall further defining a conical peripheral wall adapted to deform to be press-fitted inside the extremity of the sleeve.
  • the invention further extends to a method to assemble such actuator assembly wherein the method comprises the steps of:
  • the shaft may be provided with an annular groove as described above and, in such a case, the method further comprises, before step d) the following step:
  • the bore may be provided with two narrowing portions as described above and, in such a case, the tool provided at step b) further comprises a base plate adapted to receive the closing member, the tubular member projecting from the base plate and forming an integral centrally tubular projection and, during step c) the closing member is arranged on the base plate of the tool and is presented in face of the cylindrical sleeve and, during step d) the closing member is press-fitted inside the sleeve, the O-ring being pushed in place in the annular passage.
  • a servo actuator assembly 12 cooperates with a control valve, not represented, indirectly enabling or forbidding injection of fuel.
  • the actuator assembly 12 extends along longitudinal axis X and, it comprises an actuator member 14 enclosed in a cylindrical sleeve 16 closed at an extremity by a resilient closing member 18 and a sealing arrangement 20 defined by an axial bore 22 provided in the wall of the closing member 18, a shaft 24 of the actuator member 14 extending through the bore 22 and, an elastomeric O-ring 26 sealing the annular passage 28 between the shaft 24 and the bore 22 by being radially compressed both outwardly by the shaft 24 and inwardly by the bore 22.
  • the closing member 18 is an axisymmetric solid of revolution made by stamping a metal sheet, or other metal forming process, the constant wall thickness of the member 18 defining an outer peripheral wall 30 press-fitted and fixed, potentially by laser welding or other fixing means, inside the sleeve 16 and, an inner cylindrical tubular extension 32 which inside face defines the bore 22.
  • the O-ring In a free state the O-ring is a torus having a circular cross-section, as shown on figure 2 , an inner diameter ID and an outer diameter OD.
  • the O-ring Once in place in the sealing arrangement 20, as shown on figure 1 , the O-ring is compressed and its cross section deforms to adjust to the shaft 24 that has a shaft diameter SD superior to the inner diameter ID of the O-ring and, to the bore 22 that has a bore diameter BD smaller that the outer diameter OD of the O-ring.
  • the actuator member 14 axially expands and retracts so the shaft 24 reciprocally translates by few hundredths of millimeters along the longitudinal axis X within the bore 22 and, since fuel is present outside the actuator assembly 12 and, must not get in contact with the actuator member 14 inside the sleeve, it is crucial that the O-ring 26 perfectly seals the annular passage 28.
  • the actuator 14 when the actuator 14 expands and the shaft 24 downwardly translates, it pushes the control valve to open a discharge port through which pressurized fuel gushes generating pressure peaks in the return fuel flow flowing toward a low pressure reservoir. Under the influence of these pressure peaks, the O-ring, further deforms and compresses permanently ensuring this sealing characteristic.
  • the O-ring has dimensions chosen so it is compressed around the shaft 24 and inside the bore 22.
  • an O-ring having an inner diameter ID of 2.9 mm and an outer diameter OD of 5.25 mm can be chosen since, once in place the O-ring is radially compressed both outwardly by the shaft and inwardly by the bore.
  • a first embodiment of the sealing arrangement 20 is depicted on figure 1 where the shaft 24 and the bore 22 are parallel and concentric cylinders of revolution.
  • the O-ring 26 has deformed so its cross-section is now elongated in an oblong shape and it contacts the shaft and the bore along large contact areas.
  • the O-ring 26 rotates so that the oblong section of the O-ring represented on the right of the figure rotates in the counter-clockwise direction and the oblong section represented on the left of the figure rotates in the clockwise direction.
  • the displacements of the shaft are inferior to the large areas of contacts and also to the manufacturing tolerances of elastomeric O-rings, the rotations of the O-ring are indeed minimal and much smaller than the deformations due to the pressure peaks.
  • the rotating motion of the O-ring 26 ensures permanent sealing of the annular passage 28, it eliminates friction of the shaft inside the O-ring and it minimizes wear of the O-ring thus enhancing its longevity.
  • a presentation step 110 of the assembling method 100 of the first embodiment of the sealing arrangement 20 is represented.
  • the annular passage 28 is open; the O-ring 26 is in a free-state with non-deformed circular cross-section, simply placed on a first tool 112.
  • the O-ring 26 is presented before the annular passage 28 at the extremity of the shaft 24.
  • the first tool 112 has a tubular shape able to fully engage in the annular passage 28 and, the O-ring 26 lies on the upper annular face 114 of the first tool 112.
  • the first tool 112 moves upward and pushes the O-ring 26 inside the annular passage 28, forcing it to deform and to engage between the shaft 24 and the bore 22.
  • FIG. 3 In reference to figure 3 is described a second embodiment of the sealing arrangement 20, said second embodiment operating in a similar O-ring rolling way as the first embodiment.
  • the second embodiment of the sealing arrangement 20 only differs from the first embodiment by the shaft 24 that is provided with an annular groove 34 wherein is positioned the O-ring 26.
  • the closing member 18 remains identical to the first embodiment of figures 1 and 2 , the tubular extension 32 having a constant and non-restricted bore diameter BD.
  • the annular groove 34 has an arcuate profile intersecting the cylindrical face of the shaft in a lower edge 38 and in an upper edge 40, the longitudinal chord C of the groove 34, being measured along the axis X between the edges 38, 40.
  • the nominal dimension of the annular passage 28 is measured between the cylindrical face of the bore 22 and the bottom or center of the groove 34.
  • Fuel pressure peaks may further compress and further deform the O-ring toward an edge or even partially over an edge.
  • a third embodiment is now described in total reference to figures 4 to 7 , the third embodiment of the sealing arrangement 20 differing from the second embodiment only by the profile of the tubular extension 32 that is provided, as shown on these figures, with an upper narrowing portion 36 arranged at the inner extremity of the tubular extension 32, said inner extremity 32 being the extremity of the tubular extension that is inside the sleeve 16 closer to the actuator member 14.
  • the narrowing portion 36 may have a cylindrical shape or a conical shape.
  • This distinctive feature mainly influences the sealing arrangement 20 when fuel pressure peaks occur, as represented on figure 5 . Said pressure peaks upwardly push the O-ring which is further compressed between the shaft, which diameter increases, and the bore, which diameter decreases in the narrowing portion 36.
  • the environment of a fuel injector is chosen as an example, the sealing arrangements as described being adapted to any other applications where a shaft translates in a bore and where sealing is required.
  • the groove can accommodate other profiles such as a trapezoidal profile enabling conical portions on both sides of a flat bottom, said conical portions restricting the section of the annular passage 28.
  • a groove having a triangular profile may also fit the sealing purpose and the variation of compression of the O-ring.
  • figure 8 illustrates the presentation step 110 that is common for the second and for the third embodiments.
  • the actuator member 14 At first, inside the sleeve the actuator member 14 is in a downward position and the shaft largely protrudes below the closing member 18. In said position the O-ring is engaged around the shaft 24 where it lies radially compressed in the bottom of the groove. Then the actuator member 14 is pulled up inside the sleeve, the first tool 112 maintaining the O-ring in place in the bottom of the groove. During this upward movement, the O-ring engages in the annular passage 28 and gets compressed around the shaft and inside the bore.
  • the shaft 24 has a large circular section portion 44 and a narrow circular section portion 46, the large portion 44 being inside the sleeve 16 close to the actuator member 14 and, the narrow portion 46 largely extending in the bore and being close to the extremity of the shaft. Between these two cylindrical surfaces is a fillet 48 tangent to the narrow cylindrical surface.
  • the closing member 18 is identical to the one presented in the third embodiment, the tubular extension 32 being provided with a narrowing portion 36 arranged at the inner extremity of the tubular extension 32.
  • the O-ring rolls on the narrow circular portion 46 of the shaft and also in the cylindrical bore 22.
  • the O-ring slightly gets in the narrowing portion 36 of the bore where it is further compressed between said bore and the narrow portion 46 of the shaft and, when the shaft reaches its extreme downward position, after rolling on the narrow portion 46 of the shaft, the O-ring slightly gets on the fillet 48 and it is further compressed between said bore and the fillet 48.
  • the most important deformations of the O-ring are due to the influence of pressure peaks pushing on the O-ring deforming and getting further compressed between the fillet 48 and the narrowing portion 36 of the bore.
  • the assembly of the O-ring is similar to the method used in the first embodiment.
  • an actuator member having a similar shaft with two cylindrical portions and a fillet can cooperate in a closing member with a cylindrical tubular extension as it is on the first embodiment.
  • a superior compression value of the O-ring is only achieved when the shaft translates to a downward extreme position, the O-ring being further compressed between the cylindrical bore and the fillet.
  • a fifth embodiment is represented in reference to figures 10 and 11 .
  • the shaft 24 is similar to the shaft of the third embodiment with a large portion 44, a narrow portion 46 and a filet 48 in-between.
  • the tubular extension 32 of the closing member 18 is provided with an inner upper narrowing portion 36 similar as in the second and third embodiment and, also with an outer narrowing portion 50 arranged at the opposite end of the tubular extension 32.
  • the O-ring is arranged in place between the two narrowing portions 36, 50.
  • the O-ring rolls on the narrow portion 46 of the shaft and on the cylindrical bore 22 between said two narrowing portions 36, 50.
  • the O-ring deforms and it is pushed to get in a narrowing portion where it is further compressed.
  • a step of the assembling method is represented on figure 11 .
  • the O-ring has been firstly installed in the closing member 18, in the tubular extension between the two narrowing portions 36, 50 and, after said installation a second tool 116 having a large base plate 118 and a central tubular projection 120 similar to the first tool 112 is utilized.
  • the closing member 18 is placed on said second tool 116, the tubular projection 120 being in contact with the O-ring and, the O-ring being engaged over the narrow portion 46 of the shaft.
  • the closing member 18 is upwardly pushed inside the sleeve, said another tool 116 pushing the closing member while maintaining the O-ring in place. In this upward movement, the peripheral wall 30 of the closing member is press-fitted inside the sleeve 16.
  • the main principle of the present invention relies in the rolling movement of the O-ring when the shaft translates and also on the ability to accommodate further deformations and compressions of the O-ring when fuel pressure peaks occur.
  • Several further embodiments of the sealing arrangement combining shafts and closing members described can be assembled depending on the final need of the application.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP16176510.2A 2015-06-29 2016-06-27 Dispositif de scellement Withdrawn EP3112661A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GBGB1511355.8A GB201511355D0 (en) 2015-06-29 2015-06-29 Sealing arrangement

Publications (1)

Publication Number Publication Date
EP3112661A1 true EP3112661A1 (fr) 2017-01-04

Family

ID=53872349

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16176510.2A Withdrawn EP3112661A1 (fr) 2015-06-29 2016-06-27 Dispositif de scellement

Country Status (2)

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EP (1) EP3112661A1 (fr)
GB (1) GB201511355D0 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3208456A1 (fr) * 2016-02-16 2017-08-23 Delphi International Operations Luxembourg S.à r.l. Ensemble de buse et injecteur de carburant
US10801456B2 (en) 2015-10-27 2020-10-13 Delphi Technologies Ip Limited Control valve arrangement of a fuel injector

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000310332A (ja) * 1999-04-28 2000-11-07 Mitsubishi Electric Corp 筒内噴射用燃料噴射弁のシール機構
US6158744A (en) * 1995-07-03 2000-12-12 Smiths Industries Plc Seal arrangement providing a seal between a bore and a rod movable in the bore
DE10332088A1 (de) * 2003-07-15 2005-02-03 Robert Bosch Gmbh Brennstoffeinspritzventil
US7383818B1 (en) * 2007-04-04 2008-06-10 Gm Global Technology Operations, Inc. Fuel injector with secondary combustion seal
EP2090771A1 (fr) * 2008-02-13 2009-08-19 Robert Bosch Gmbh Injecteur de carburant doté d'un pointeau de soupape commandé directement
DE102009001989A1 (de) * 2008-03-31 2009-10-01 Denso Corporation, Kariya-City Injektor
US20110303192A1 (en) * 2007-05-02 2011-12-15 Klaus Jung Internal combustion engine with sealing protection for a fuel injection valve
DE102011086335A1 (de) * 2011-11-15 2013-05-16 Robert Bosch Gmbh Brennstoffeinspritzventil

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6158744A (en) * 1995-07-03 2000-12-12 Smiths Industries Plc Seal arrangement providing a seal between a bore and a rod movable in the bore
JP2000310332A (ja) * 1999-04-28 2000-11-07 Mitsubishi Electric Corp 筒内噴射用燃料噴射弁のシール機構
DE10332088A1 (de) * 2003-07-15 2005-02-03 Robert Bosch Gmbh Brennstoffeinspritzventil
US7383818B1 (en) * 2007-04-04 2008-06-10 Gm Global Technology Operations, Inc. Fuel injector with secondary combustion seal
US20110303192A1 (en) * 2007-05-02 2011-12-15 Klaus Jung Internal combustion engine with sealing protection for a fuel injection valve
EP2090771A1 (fr) * 2008-02-13 2009-08-19 Robert Bosch Gmbh Injecteur de carburant doté d'un pointeau de soupape commandé directement
DE102009001989A1 (de) * 2008-03-31 2009-10-01 Denso Corporation, Kariya-City Injektor
DE102011086335A1 (de) * 2011-11-15 2013-05-16 Robert Bosch Gmbh Brennstoffeinspritzventil

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10801456B2 (en) 2015-10-27 2020-10-13 Delphi Technologies Ip Limited Control valve arrangement of a fuel injector
EP3208456A1 (fr) * 2016-02-16 2017-08-23 Delphi International Operations Luxembourg S.à r.l. Ensemble de buse et injecteur de carburant

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Publication number Publication date
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