EP1428990A1 - Etanchéité de boisseau rotatif - Google Patents

Etanchéité de boisseau rotatif Download PDF

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Publication number
EP1428990A1
EP1428990A1 EP03028002A EP03028002A EP1428990A1 EP 1428990 A1 EP1428990 A1 EP 1428990A1 EP 03028002 A EP03028002 A EP 03028002A EP 03028002 A EP03028002 A EP 03028002A EP 1428990 A1 EP1428990 A1 EP 1428990A1
Authority
EP
European Patent Office
Prior art keywords
sealing ring
sealing
slide valve
rotary slide
valve part
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Withdrawn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
EP03028002A
Other languages
German (de)
English (en)
Inventor
Christoph Conradty
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP1428990A1 publication Critical patent/EP1428990A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/16—Sealing or packing arrangements specially therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2301/00—Using particular materials
    • F01L2301/02—Using ceramic materials

Definitions

  • the invention relates to a seal between the relatively rotatable parts of a rotary slide valve.
  • the seal between the two rotatable relative to each other Part of a rotary slide valve has the function, both in the closed position and also in the open position of the rotary slide valve and in any intermediate position prevent fluid across the gap between the two relative to each other can leak rotatable parts.
  • the function can be just as important be the penetration of foreign substances such as lubricating oil through the gap between the parts of the rotary slide valve which can be rotated relative to one another into those of the rotary slide valve to prevent influenced fluid channels.
  • the present invention has particular, if not exclusive, application of rotary slide valves as intake and exhaust valves in piston internal combustion engines in view of what has been known for a long time (e.g. CH-PS 222 337 from the Years 1943).
  • the sealing ring has a cylindrical ring shape with a lower end face facing away from the rotary valve body and the cylindrical one Roll contour of the rotary valve body corresponding to the curved upper, the rotary valve body facing end face, and it is supported by a plurality of between groove bottom and sealing ring each seated in blind holes of the sealing ring Helical compression springs held in contact with the rotary valve body, the can consist, among other things, of a ceramic material.
  • the object of the invention is to provide an improved sealing arrangement between a rotary valve housing and a rotary valve body rotatable relative thereto in the area of a To create opening of the housing or the rotary valve body.
  • the sealing arrangement of the housing opening can be assigned if this is the Inlet opening or outlet opening of the cylinder forms. But they are also use cases conceivable, on which the rotary valve body is fixed and the sealing arrangement is assigned to the rotary valve body opening and the rotary valve housing is relative to the rotary valve body.
  • the sealing arrangement according to the invention uses the fluid pressure in the Flow channel or in the opening surrounded by the sealing arrangement for generation or support of the contact pressure of the sealing ring on the counter surface.
  • the system pressure generated in each case is therefore dependent on the fluid pressure.
  • the sealing contact pressure In order to the sealing contact pressure is only as large as it is under the given Pressure conditions for a reliable seal is necessary. With the above State of the art, however, the selected contact pressure must be so large that it in the worst case is sufficient for a clean seal.
  • the sealing arrangement according to the invention thus has several advantages. On the one hand, it does not apply the need for sufficiently strong springs to ensure a clean seal to ensure the contact pressure of the sealing ring on the counter surface, but the invention only requires a relatively small basic prestressing of the sealing ring, around this at all from the groove receiving it in contact with the Lift the counter surface. This means that there is significantly less space required in the groove required, which also reduces the necessary expansion of the groove. Furthermore is at the sealing arrangement according to the invention the risk of malfunction in the form of the risk of Broken springs due to overload or fatigue as well as the risk of Fatigue or wear and tear of the springs, which changes the pressure properties, is eliminated. The stress on the sealing ring end face and / or the sealing counter surface is reduced on average and thereby the possible wear reduced.
  • Sealing arrangement expediently between the bottom of the groove and the sealing ring can be arranged, which produces only a lower basic bias, so that Sealing ring does not "fall” into the sealing groove, which is already due to the fact that necessary tolerances the sealing ring must allow some play.
  • This leaf spring therefore only has to exert a small force and a small spring travel and can therefore be made smaller and is far less likely to break or subjected to operational changes in the spring characteristic than this the conventional sealing arrangement mentioned above is the case.
  • Fig. 1 shows an exploded view of an approximately cylindrical valve spool body 1 with a lateral surface 11 and a valve channel 12 with a first opening 13 and a diametrically opposite but axially offset second Mouth opening 14, further a housing component in the form of a half-shell 2 with a Opening 21, which with the mentioned first opening 13 of the valve channel 12 of the Rotary slide body 1 cooperates, and a receiving groove surrounding the opening 21 22 for a sealing ring, further a sealing ring 3, which in the receiving groove 22 of the half-shell 2 is to be used, and an annularly shaped leaf spring 4 which between the groove base and the sealing ring 3 into the receiving groove 22 of the half-shell 2 is to be inserted.
  • the opening 21 of the half-shell is just like the mouth opening 13 of the Rotary vane body 1 is not circular, but in each appropriately selected Wise oval or elongated.
  • the receiving groove 22, the sealing ring 3 and the leaf spring 4th have an appropriate shape.
  • the sealing ring 3 is, as FIG. 2 shows as detail II of the illustration in FIG. 1, on one Slotted at the circumference, but formed with gas-tight overlapping ends 31, 32, so that changes in the circumferential length, for example, by thermal expansion movements can be recorded without accompanying radial movement.
  • the leaf spring 4 can be slightly corrugated in the circumferential direction and is designed so that it only exerts a weak pretensioning force on the sealing ring 3 in order to remove it from the groove base area to lift out into contact with the lateral surface 11 of the rotary valve body 1.
  • the housing in which the rotary valve body 1 is rotatably seated is not shown in detail. It is expediently divided axially and in which the outer surface of the rotary valve body 1 surrounding area formed with half-shells, one of which as a half-shell 2 is shown.
  • the housing forms part of the cylinder head, and the opening 21 of the half-shell 2 together with a corresponding opening of the adjacent housing part communicates with the cylinder.
  • FIG. 3 shows an enlarged schematic section through the arrangement of rotary valve body 1 and part of a cylinder head forming housing 20, here for the sake of simplicity, the half-shell 2 is not specifically shown, and that in the Receiving groove 22 seated sealing ring 3.
  • the leaf spring 4 from FIG. 1 is for simplicity also not shown in FIG. 3, because FIG. 3 is primarily intended to explain the function.
  • FIG. 3 shows that the receiving groove 22 is larger both in its width and in its depth than the sealing ring 3 is that further the sealing ring on the radially outer groove wall abuts and a space between the radially inner groove wall and the sealing ring and that there is also a space between the bottom of the sealing ring and the groove bottom of the receiving groove 22.
  • Fig. 3 further shows that the cylinder space Via the opening 21 and the gap between the housing 20 and the rotary valve body 1 connection with the free interior parts of the receiving groove radially inside and below the sealing ring 3 has.
  • the pressure of the medium in the cylinder therefore affects both radially inner surface of the sealing ring and on the lower end face of the sealing ring and thus exerts both a radial contact pressure against the outer groove wall also against a contact pressure acting on the lower end face of the sealing ring the surface area 11 of the rotary valve body 1.
  • the stronger the pressure in the cylinder the more the contact force with which the sealing ring 3 is pressed against the lateral surface 11 is therefore stronger of the rotary valve body 1 is pressed.
  • Fig. 4 shows a representation similar to Fig. 3 with additional advantageous features of Sealing ring 3.
  • the one facing the rotary valve body 1 modified end face of the sealing ring 3 modified.
  • a radially inner one Section 33 of the sealing face is slightly chamfered so that it is flush with the mantle 11 of the rotary valve body 1 forms a tapering gap, in the widened Area of pressure can get in from the combustion chamber and thereby a quasi Non-contact contact of the remaining part 34 of the sealing face is generated in the a minimal gas cushion between this surface area of the outer surface of the rotary valve body is produced.
  • This sealing surface area 34 of the sealing ring end face is preferably provided with a special diamond coating 35, the one hard, wear-resistant surface results.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Taps Or Cocks (AREA)
EP03028002A 2002-12-06 2003-12-05 Etanchéité de boisseau rotatif Withdrawn EP1428990A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10257046 2002-12-06
DE10257046A DE10257046A1 (de) 2002-12-06 2002-12-06 Drehschieberdichtung

Publications (1)

Publication Number Publication Date
EP1428990A1 true EP1428990A1 (fr) 2004-06-16

Family

ID=32318986

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03028002A Withdrawn EP1428990A1 (fr) 2002-12-06 2003-12-05 Etanchéité de boisseau rotatif

Country Status (2)

Country Link
EP (1) EP1428990A1 (fr)
DE (1) DE10257046A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009047566A1 (fr) * 2007-10-12 2009-04-16 Gordon Mcnally Joint d'étanchéité pour une vanne rotative pour un moteur à combustion interne
WO2011015648A3 (fr) * 2009-08-07 2011-07-21 Behr Gmbh & Co. Kg Vanne de rotation et pompe à chaleur
ITPA20100018A1 (it) * 2010-04-20 2011-10-21 Vincenzo Adamo Sistema di distribuzione a flauti.
EP2573337A1 (fr) 2011-09-23 2013-03-27 Arno Hofmann Agencement d'une soupape à tiroir et d'un système d'étanchéité pour l'étanchéification de la soupape à tiroir dans un moteur thermique

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005000034A1 (de) * 2005-04-15 2006-10-19 Ford Global Technologies, LLC, Dearborn Drehschieberventil für ein Kraftfahrzeug

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2109856A (en) * 1981-11-14 1983-06-08 Richard Furneaux Kinnersly Internal combustion engine rotary valves
US4449721A (en) * 1980-12-18 1984-05-22 Tokico Ltd. Split piston ring having stepped ends
DE4017819A1 (de) * 1989-06-21 1991-01-17 Ficht Gmbh Ringdichtung fuer den kugelkoerper eines im zylinderkopf eines verbrennungsmotors gelagerten kugeldrehschiebers
US5129688A (en) * 1990-08-10 1992-07-14 General Components, Inc. Torque reducing coupling for face seal fittings
US5154147A (en) * 1991-04-09 1992-10-13 Takumi Muroki Rotary valve
EP0675303A1 (fr) * 1994-03-30 1995-10-04 Cummins Engine Company, Inc. Garniture mécanique d'étanchéité pour pompe de liquide de refroidissement d'un moteur à combustion interne
US6321699B1 (en) * 1997-08-25 2001-11-27 Richard Berkeley Britton Spheroidal rotary valve for combustion engines

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH222337A (de) * 1940-05-29 1942-07-15 Heylandt Paul Dr Ing E H Dichtungseinsatz für durch walzenförmige Drehschieber gesteuerte Brennkraftmaschinen.
DE919378C (de) * 1951-09-19 1954-10-21 Rudolf Burkhardt Dipl Ing Kugeldrehschieber fuer Verbrennungskraftmaschinen
DE10032721A1 (de) * 2000-07-05 2002-01-17 Arno Hofmann Dichtungssystem

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4449721A (en) * 1980-12-18 1984-05-22 Tokico Ltd. Split piston ring having stepped ends
GB2109856A (en) * 1981-11-14 1983-06-08 Richard Furneaux Kinnersly Internal combustion engine rotary valves
DE4017819A1 (de) * 1989-06-21 1991-01-17 Ficht Gmbh Ringdichtung fuer den kugelkoerper eines im zylinderkopf eines verbrennungsmotors gelagerten kugeldrehschiebers
US5129688A (en) * 1990-08-10 1992-07-14 General Components, Inc. Torque reducing coupling for face seal fittings
US5154147A (en) * 1991-04-09 1992-10-13 Takumi Muroki Rotary valve
EP0675303A1 (fr) * 1994-03-30 1995-10-04 Cummins Engine Company, Inc. Garniture mécanique d'étanchéité pour pompe de liquide de refroidissement d'un moteur à combustion interne
US6321699B1 (en) * 1997-08-25 2001-11-27 Richard Berkeley Britton Spheroidal rotary valve for combustion engines

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009047566A1 (fr) * 2007-10-12 2009-04-16 Gordon Mcnally Joint d'étanchéité pour une vanne rotative pour un moteur à combustion interne
WO2011015648A3 (fr) * 2009-08-07 2011-07-21 Behr Gmbh & Co. Kg Vanne de rotation et pompe à chaleur
JP2013501205A (ja) * 2009-08-07 2013-01-10 ベール ゲーエムベーハー ウント コー カーゲー 回転バルブおよびヒートポンプ
US8826684B2 (en) 2009-08-07 2014-09-09 Behr Gmbh & Co. Kg Rotating valve and heat pump
ITPA20100018A1 (it) * 2010-04-20 2011-10-21 Vincenzo Adamo Sistema di distribuzione a flauti.
EP2573337A1 (fr) 2011-09-23 2013-03-27 Arno Hofmann Agencement d'une soupape à tiroir et d'un système d'étanchéité pour l'étanchéification de la soupape à tiroir dans un moteur thermique
WO2013041233A1 (fr) 2011-09-23 2013-03-28 Arno Hofmann Ensemble d'une soupape à tiroir et d'un système d'étanchéité permettant d'assurer l'étanchéité de la soupape à tiroir sur un moteur thermique

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DE10257046A1 (de) 2004-06-24

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