EP2619486A1 - Liaison étanche optimisée en termes de tolérance et procédé de fabrication - Google Patents

Liaison étanche optimisée en termes de tolérance et procédé de fabrication

Info

Publication number
EP2619486A1
EP2619486A1 EP11740946.6A EP11740946A EP2619486A1 EP 2619486 A1 EP2619486 A1 EP 2619486A1 EP 11740946 A EP11740946 A EP 11740946A EP 2619486 A1 EP2619486 A1 EP 2619486A1
Authority
EP
European Patent Office
Prior art keywords
pin
support frame
elastomer
hole
elastomeric
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Withdrawn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
EP11740946.6A
Other languages
German (de)
English (en)
Inventor
Ralf Salameh
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.)
Federal Mogul Sealing Systems GmbH
Original Assignee
Federal Mogul Sealing Systems GmbH
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 Federal Mogul Sealing Systems GmbH filed Critical Federal Mogul Sealing Systems GmbH
Publication of EP2619486A1 publication Critical patent/EP2619486A1/fr
Withdrawn legal-status Critical Current

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
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/021—Sealings between relatively-stationary surfaces with elastic packing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
    • B23P19/00—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes
    • B23P19/04—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes for assembling or disassembling parts
    • 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
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/061—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with positioning means
    • 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
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
    • F16J15/0818—Flat gaskets
    • 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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B2200/00—Constructional details of connections not covered for in other groups of this subclass
    • F16B2200/60—Coupler sealing means
    • 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
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
    • F16J15/0818—Flat gaskets
    • F16J2015/0856—Flat gaskets with a non-metallic coating or strip
    • 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
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
    • F16J15/0818—Flat gaskets
    • F16J2015/0868—Aspects not related to the edges of the gasket
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49826—Assembling or joining

Definitions

  • the present invention relates to an improved seal, in particular carrier frame seal, with regard to the determination and compliance of position! réelles- or assembly tolerances is optimized, and a corresponding manufacturing process.
  • the elastomeric pin is chosen as the zero point, there is the metrological problem that the elastomeric pin usually has a relatively small diameter, and in addition of course is flexible, since it consists of elastomer. In addition, influences such as material shrinkage and deformation make alignment with the elastomeric pin very difficult and challenge the measurement of the entire component.
  • the component essentially the hole pattern and thus also the position of the sealing lips
  • the component can be detected very well by measuring, but there is then an additional measuring path with tolerance up to the molded elastomeric pin, which is often due to The low flange coverage often can not be accepted.
  • the pin is sprayed onto the metallic surface of the support frame.
  • a channel is generally impressed, over which the pin is filled with elastomer.
  • the center of the pin lies above this surface or on the support frame on this embossed surface. If the center is defined at this point, it can not be detected in principle on the component by measurement, since it is defined graphically on a flat surface and thus lies on a sheet metal surface.
  • Task is therefore to develop a solution that no longer has all these disadvantages and ensures an ideal functional interaction and can also be metrologically well checked and displayed.
  • Subassemblies such as e.g. The support frame of a seal should be integrated.
  • the invention described below relates to a carrier frame seal and a manufacturing method of which makes it possible to implement all mentioned specifications and thus to set the zero point in the region of the centering pin, without taking the known and described disadvantages into account.
  • a carrier frame seal comprising:
  • the support frame has a through hole that is aligned with the at least one elastomer pin.
  • the at least one elastomer pin is made solid. According to one embodiment, the at least one elastomeric pin has a through hole that aligns with the associated through hole in the carrier frame.
  • the at least one elastomeric pin extends partially into the associated through hole so that only the inner edge of the associated passage hole is covered with elastomer.
  • the at least one elastomer pin has an undercut. As a result, a captive can be provided.
  • the at least one elastomer pin is designed in one piece with the at least one sealing element.
  • a carrier frame seal comprising:
  • the at least one elastomer pin is made solid.
  • the method further comprises, after providing the support frame with the at least one through-hole:
  • the molding of the at least one elastomeric pin is carried out so that only the inner edge of the associated through-hole is covered with elastomer.
  • the molding of the at least one elastomeric pin is carried out so that the at least one elastomeric pin receives an undercut.
  • the at least one sealing element and the at least one elastomer pin are integrally molded together.
  • Fig. 1 is a plan view of a support frame of a conventional support frame seal
  • Fig. 2 shows a cross section of the carrier frame seal of Fig. 1;
  • FIG. 3 shows a plan view of a support frame of a support frame seal according to a first embodiment of the invention
  • Fig. 4 shows the carrier frame seal of Figure 3 in cross section.
  • Fig. 5 shows a carrier frame seal according to a second embodiment of the invention in cross section
  • Fig. 6 shows a carrier frame seal according to a third embodiment of the invention in cross section. Detailed description of the invention
  • Fig. 1 shows a plan view of a part of the support frame 2 of a conventional carrier frame seal.
  • an elastomer pin will be located at the finished carrier frame seal.
  • the elastomer pin should then be molded in one piece together with the elastomer sealing element.
  • a channel-like depression or impression is provided in order for elastomer to reach the point indicated by X safely and thus the elastomer pin can be formed.
  • the problem with this conventional seal is that the position of the elastomeric pin is not directly measurable because it lies in the sheet metal plane.
  • FIG. 2 shows a cross section along the dash-dotted line in FIG. 1, with the sealing element 6 and elastomer pin 4 already molded in. It should be noted that the right side in this figure corresponds to the inner edge of the support frame of FIG.
  • the only way to measure the zero point of the elastomeric pin is to measure the pin itself or its tip. As explained above, this does not allow a safe measurement, among other things because of the flexible properties of the elastomer and the distance between pin tip and plane of the screw holes etc. in the support frame, which introduces additional undesirable tolerances.
  • the present invention proposes an improved carrier frame seal.
  • a first embodiment is shown in plan view in FIG.
  • the support frame 2 of a corresponding seal is provided with an additional through-hole 8 at the position of the elastomeric pin to be molded.
  • Fig. 4 the embodiment of Fig. 3 with already molded sealing element 6 and elastomer pin 4 is shown in cross section. It is noted that the right-hand side in the figures corresponds to the inner edge of the support frame of FIG. 3.
  • the elastomer pin 4 is solid in this example, ie closes above the plane of the support frame 2, the passage opening 8.
  • the support frame of the seal must reasonably have the zero point as the basis of the measurement of hole pattern and seal geometry at the location of the centering pin (zero point seal).
  • the zero point on the support frame is at this point according to the invention metrologically defined by the fact that the support frame 2 at this point an additional opening 8 is stamped. On the basis of this opening 8, the zero position can now be clearly defined and measured.
  • this opening 8 can be punched together according to one embodiment with the screw holes, is preferably round and has, for example, a diameter of about 3 mm.
  • the elastomeric injection tool into which the support frame 2 is inserted in order to inject the elastomeric sealing lips 6 and the centering and fastening pins 4 must have a special design in the region of the centering pin 4 which marks the zero point.
  • the support frame 2 must be fixed exactly at the point "zero point of support frame and later seal" in the tool so that minimal tolerances between the molded centering pin 4 and the punched hole pattern of the seal arise.
  • the tool is carried out at this point so that a metallic pin, for example, engages in the opening 8 of the support frame 2 and securely locates and fixes the sheet metal part.
  • the pin is advantageously rounded at the protruding from the tool side or has an insertion bevel so that the support plate 2 can be easily positioned.
  • the coordination between the centering pin and the hole diameter in the carrier plate 2 is selected such that a very thin elastomer layer 10 is formed between the centering pin 4 and the carrier plate 2 during the injection of the elastomer.
  • This layer can range from a few hundredths of a millimeter to a few tenths of a millimeter be thick and is chosen exactly so that it is closed circumferentially, but not thicker than absolutely necessary to map this closed elastomeric circle around the fixing pin 4.
  • This very thin elastomer layer 10 has various tasks.
  • the elastomer layer 10 between centering pin 4 and sheet metal frame 2 ensures good mold release of the finished component. For purely metallic contact larger tolerances would have to be chosen to prevent jamming of the component.
  • this elastomer layer 10 Another important function of this elastomer layer 10 is the direct dependence and immutability of the assignment between the elastomer layer 10 and the centering pin 4, since both are exactly specified in the tool and their relative position is thereby fixed exactly. This means that the position of the, for example, circular elastomer layer 10 in the opening directly below the elastomer pin 4 coincides exactly with the position and position of the zero point and thus of the overlying centering pin 4. After the removal of the seal from the tool is located exactly at the point of zero on the opposite side of the centering pin 4, a circular opening 8 at the precise now the zero point for the survey can be determined.
  • a significant advantage of this solution is also that with a very thin elastomer layer 10 in the opening, this is supported by the directly underlying support frame 2 and has virtually no flexibility due to the incompressible material behavior of elastomers in the thin layer.
  • this thin elastomer layer 10 is also vulcanized to the support frame 2 like all other elastomer areas.
  • the support plate 2 is also directly at the point at which the elastomeric centering pin 4 (zero point) sits, with a corresponding - for example, circular, but generally at least point-symmetrical - opening 8 in the support plate 2 executed.
  • the corresponding production tool is designed so that the sheet 2 can be taken exactly at this point via a pin and centered.
  • the inner region 12 of the pin 4 is kept free during the injection of the elastomer and not filled with elastomer via the injection molding tool. This results even after the injection of the pin 4, the possibility to use the opening 8 in the support plate 2 for determining the zero point.
  • the centering pin 4 with respect to the opening 8 in the support plate 2 have so little "game” that this just barely installed and demould after the injection process again.
  • a third exemplary embodiment which is shown in cross section in FIG. 6, elements of the two embodiments described above are combined.
  • the pin 4 is designed as in the second embodiment of FIG. 5 inside with a cavity 12.
  • the opening 8 in the support plate 2 as in the first embodiment when injecting the elastomer with a very thin elastomer pad 10 is provided.
  • a seal according to the invention can also have a plurality of elastomer pins, which can either all be located on the same side of the support frame or on different or opposite sides.
  • the position and shape of the sealing element is not limited to the exemplary shape in Figures 4 to 6, but may also be designed differently.
  • the sealing element may be provided instead of on the inner edge of the support frame or additionally on one or both sides of the support frame.
  • the sealing element does not necessarily have to be made in one piece with the elastomeric pin (s).
  • the invention can be used in general for all types of girder seals, for example for girder seals for oil sumps.
  • the invention offers, inter alia, the following advantages.
  • An optimal tolerance-side design of a module "oil pan with seal" is made possible, eliminating the influence of different zero points on components and on the finished part, as well as eliminating the effects of measurements on flexible elastomer pins consist.
  • An optimal measurement of girder seals with respect to the following important tolerance dimensions is guaranteed.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Injection Moulding Of Plastics Or The Like (AREA)
  • Gasket Seals (AREA)

Abstract

L'invention concerne un joint d'étanchéité de cadre de support, comprenant : un cadre de support (2) muni d'au moins une ouverture traversante intérieure ; au moins un élément d'étanchéité (6) qui entoure l'ouverture traversante intérieure ; et au moins une broche en élastomère (4) faisant saillie d'un premier côté du cadre de support (2), le cadre de support comportant un trou débouchant (8) aligné avec la ou les broches en élastomère.
EP11740946.6A 2010-09-20 2011-08-09 Liaison étanche optimisée en termes de tolérance et procédé de fabrication Withdrawn EP2619486A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010041067A DE102010041067A1 (de) 2010-09-20 2010-09-20 Toleranzoptimierter Dichtverbund und Herstellungs-Verfahren
PCT/EP2011/063693 WO2012038147A1 (fr) 2010-09-20 2011-08-09 Liaison étanche optimisée en termes de tolérance et procédé de fabrication

Publications (1)

Publication Number Publication Date
EP2619486A1 true EP2619486A1 (fr) 2013-07-31

Family

ID=44629817

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11740946.6A Withdrawn EP2619486A1 (fr) 2010-09-20 2011-08-09 Liaison étanche optimisée en termes de tolérance et procédé de fabrication

Country Status (5)

Country Link
US (1) US8876117B2 (fr)
EP (1) EP2619486A1 (fr)
CN (1) CN103328868A (fr)
DE (1) DE102010041067A1 (fr)
WO (1) WO2012038147A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9909440B2 (en) 2011-03-24 2018-03-06 Dresser-Rand Company Interlocking hole pattern seal
JPWO2017154615A1 (ja) * 2016-03-08 2019-01-17 Nok株式会社 ガスケット及び密封装置
DE202018105005U1 (de) * 2018-04-30 2019-07-31 Reinz-Dichtungs-Gmbh Gehäuseintegration

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US2576673A (en) * 1946-09-09 1951-11-27 Prentiss I Cole Fluid seal
DE3310893C2 (de) * 1983-03-25 1985-12-05 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Dichtung
US4757560A (en) * 1985-01-08 1988-07-19 Kohler Co. Toilet tank gasket
US4602125A (en) * 1985-05-10 1986-07-22 The Bergquist Company Mounting pad with tubular projections for solid-state devices
US4867461A (en) * 1988-03-01 1989-09-19 J. L. French Corporation Gasket sealing system
US5513603A (en) * 1995-08-11 1996-05-07 Chrysler Corporation Seal and fastener isolator system for a valve cover
DE10025658B4 (de) * 2000-05-24 2008-07-03 Deutz Ag Brennkraftmaschine mit einem staubdicht verschlossenen Zahnriemenraum
DE10100934C1 (de) * 2001-01-10 2002-02-28 Freudenberg Carl Kg Anordnung zur gasdichten Befestigung eines einen Verbindungsflansch aufweisenden Ansaugkrümmers am Zylinderkopf einer Verbrennungskraftmaschine
US6676135B2 (en) * 2002-04-03 2004-01-13 General Motors Corporation Oil transfer seal assembly
WO2005023452A1 (fr) * 2003-08-26 2005-03-17 Parker-Hannifin Corporation Systeme de joint de retenue
DE102004027843A1 (de) * 2004-06-08 2006-01-05 Federal-Mogul Sealing Systems Bretten Gmbh Trägerrahmendichtung mit Befestigungsmitteln zur Abdichtung von Motorbauteilen
DE102007063657B4 (de) * 2007-04-28 2012-06-14 Elringklinger Ag Baugruppe, umfassend eine Dichtung und mindestens eine Verbindungsanordnung zum Verbinden der Dichtung und eines die Dichtung haltenden Bauteils
CN102770695B (zh) * 2009-12-18 2015-02-25 费德罗-莫格尔公司 具有改进的定位和固位钉的密封垫组件及其构造方法

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Title
See references of WO2012038147A1 *

Also Published As

Publication number Publication date
WO2012038147A1 (fr) 2012-03-29
CN103328868A (zh) 2013-09-25
US8876117B2 (en) 2014-11-04
US20130183083A1 (en) 2013-07-18
DE102010041067A1 (de) 2012-03-22

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