EP0797743A1 - Joint de segment de piston - Google Patents

Joint de segment de piston

Info

Publication number
EP0797743A1
EP0797743A1 EP95940986A EP95940986A EP0797743A1 EP 0797743 A1 EP0797743 A1 EP 0797743A1 EP 95940986 A EP95940986 A EP 95940986A EP 95940986 A EP95940986 A EP 95940986A EP 0797743 A1 EP0797743 A1 EP 0797743A1
Authority
EP
European Patent Office
Prior art keywords
piston
piston ring
ring
conical
ring seal
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Withdrawn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
EP95940986A
Other languages
German (de)
English (en)
Inventor
Hermann Meckes
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 EP0797743A1 publication Critical patent/EP0797743A1/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Withdrawn legal-status Critical Current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
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F16J9/20—Rings with special cross-section; Oil-scraping rings

Definitions

  • the invention relates to a piston ring seal, in particular for internal combustion engines, with a piston ring arranged in the upper end area of a piston on the combustion chamber side, which has a radially concave, cone-shaped inner surface which interacts with a correspondingly adapted radially convex, cone-shaped annular surface of a piston, wherein the conical annular surface of the piston is arranged offset radially inwards and the piston ring rests against the cylinder wall of a cylinder in which the piston is guided so as to be axially movable.
  • a piston ring seal has a piston ring on the combustion chamber side, which in most known designs is arranged at a distance from the piston chamber surface on the combustion chamber side in a circumferential piston ring groove of the piston jacket surface.
  • the piston forms with the cylinder surrounding it, in which the piston is guided so as to be axially movable, a circumferential gap, the top land gap.
  • the piston ring has both axial and radial play in the piston ring groove, so that corresponding circumferential gap spaces also result here.
  • Fuel-air mixture is pressed into these gap spaces during the compression stroke, as a result of which the piston ring is pressed axially on the one hand in the direction of the crankcase of an internal combustion engine opposite the combustion chamber and on the other hand radially against the cylinder wall of the cylinder.
  • the fuel-air mixture located in the top land and in the above-mentioned gap spaces cannot burn completely, so that the exhaust gases of an internal combustion engine equipped with this known piston ring seal contain a relatively high proportion of pollutants.
  • Piston ring seals have also become known (US Pat. No. 1,711,610) in which a piston ring is arranged in the upper end region of a piston on the combustion chamber side.
  • the piston In order to receive the piston ring, the piston is formed so as to be offset radially inward in its upper end region and has a circumferential radial web for receiving the piston ring below its upper piston chamber-side piston surface within this radial shoulder.
  • This radial web is provided with a conical surface which widens radially from top to bottom from the combustion chamber side, on which the piston ring is provided with a suitably shaped receiving groove fits.
  • the receiving groove of the piston ring is accordingly arranged on its inner surface and its shape is identical to that of the radial web with its conical seat surface and accordingly also has a conical seat surface which widens radially from the combustion chamber side from top to bottom.
  • the piston ring lies completely against the piston, so that the radial web of the piston is completely received by the receiving groove of the piston ring and the radially outer lateral surface of the piston ring forms a common cylindrical lateral surface with the outer lateral surface of the piston.
  • the piston ring In operation, the piston ring is displaced in the axial direction from the combustion chamber side as soon as it is subjected to compression pressure or combustion pressure on the combustion chamber side of its ring surface, and due to the arrangement of the conical surfaces on the one hand the radial web and on the other hand the receiving groove of the Expanded piston ring and accordingly pressed against the cylinder wall of a cylinder in which the piston is axially movable.
  • This radial expansion of the piston ring creates a circumferential annular gap between the piston ring and the piston above the radial web or above the receiving groove of the piston ring, which extends from the piston surface in the axial direction down to Radial web extends.
  • a piston ring is provided, which is also arranged in the upper end region of a piston on the combustion chamber side.
  • the piston forms a circumferential groove for receiving the piston ring, which is provided with a lower oblique, conical groove delimitation surface.
  • the piston ring is fitted with an upper circumferential circumferential piston ring surface running transversely to the longitudinal axis of the piston in this circumferential groove of the piston ring.
  • the shape of the piston ring is u Fenden groove of the piston adapted and accordingly has a lower conical surface, the inclination of which corresponds to the inclination of the groove boundary surface of the circumferential groove.
  • the invention has for its object to improve a piston ring seal of the generic type such that with the greatest possible tightness between Pistons and cylinders reduce the exhaust gas emissions of an internal combustion engine to a minimum.
  • the object is achieved in that the conical inner surface of the piston ring extends to its upper piston ring surface on the combustion chamber side, and in that the conical annular surface area of the piston extends to the upper piston surface on the combustion chamber side, so that the upper ring surface of the piston ring on the combustion chamber side at least during the Compression and working stroke of the piston forms a common, gapless compression surface with the piston surface of the piston on the combustion chamber side.
  • the design according to the invention provides a piston ring seal in which a circumferential gap does not occur between the piston and the piston ring, nor between the piston and the cylinder wall of the cylinder, in which the piston is axially movably guided. This effectively prevents that fuel-air mixture can accumulate in an uncontrolled manner, at least during the compression and working stroke in the operation of an internal combustion engine. Because of this gapless design of the compression surface, the fuel / air mixture cannot accumulate anywhere in an uncontrolled manner in the combustion chamber of an internal combustion engine, particularly during the compression stroke, so that As complete a combustion as possible is ensured during the work cycle and the pollutant content in the exhaust gas can thereby be kept extremely low.
  • the piston ring is always pressed outwards against the cylinder wall both during the compression, working and exhaust stroke and during the suction stroke of the piston by the interaction of the upper and lower conical surfaces of the piston and the piston ring of the cylinder, so that the piston ring seal according to the invention has an increased degree of tightness.
  • an absolute tightness of the piston ring is achieved in the region of the piston ring joint.
  • the piston ring in the area of the piston ring joint with its overlapping components is designed with sharp edges, so that no gap is formed between the piston ring and the cylinder wall and thus absolute tightness is ensured.
  • the embodiment according to claim 4 also serves to improve the tightness, in which the joint gap of the butt joint of the piston ring joint ensures gas tightness with about 0.01 mm.
  • the configuration according to claim 6 ensures that there are no annular gaps between the piston or piston ring and the cylinder wall, so that this also ensures extremely low-pollutant combustion.
  • a piston tilting is effectively prevented by the configuration according to claim 7.
  • the piston ring seal can be easily adapted to different operating conditions in different internal combustion engines. Due to the size of the cone angles ⁇ and ⁇ , the radial contact pressure can be preselected as a function of the combustion pressure or compression pressure during operation of the internal combustion engine via the cone angles ⁇ and ⁇ .
  • the cone angles .alpha. And .beta. Of the conical surfaces can also be of the same size and be approximately 45 °.
  • the configuration according to claim 10 effectively prevents the piston ring from fluttering, since due to the spring elements provided, the upper cone surface of the piston ring constantly rests on the upper conical surface of the piston and thus a relative axial movement the piston ring with respect to the piston is excluded.
  • the piston ring is pressed axially downwards as well as radially outwards against the cylinder wall, so that the piston ring cannot be made round, as is usually the case, since it is constantly pressed against the cylinder wall by the helical compression spring and thus no radial prestressing of the piston ring is necessary, as is provided in conventional designs of piston ring seals.
  • FIG. 1 is a piston ring seal of the type according to the invention in partial section.
  • FIG. 2 shows an embodiment of a piston ring seal according to FIG. 1 with additional screw pressure springs /
  • FIG. 3 shows an embodiment of a piston ring seal with an axially offset piston ring
  • FIG. 4 shows a piston ring in side view with a double overlapping piston ring joint
  • FIG. 5 shows a bottom view of a piston ring with spring tongues integrally formed thereon
  • FIG. 6 is a partial view of the piston ring VI from FIG. 5;
  • FIG. 7 shows a piston ring seal in partial section with the piston ring according to FIG. 5.
  • a piston ring seal 1 according to the invention, consisting of a piston ring 2, which is arranged in the region of the upper end of a piston 3 on the combustion chamber side.
  • the piston 3 is guided in an axially movable manner in a cylinder 4, the piston 3 delimiting a combustion chamber 14 in the cylinder 4 downwards and separating the combustion chamber 14 from the crankcase of an internal combustion engine (not shown in the drawing).
  • the piston 3 is embodied at its upper end on the combustion chamber side and has one circumferential receiving paragraph 5 for the piston ring 2.
  • the receiving shoulder 5 is provided with a radially outwardly directed circumferential ring web 6, on which the piston ring 2 is positively and axially movably supported.
  • the annular web 6 is double-wedge-shaped in cross section and has an upper annular conical surface 7 and a lower conical surface 8.
  • the circumferential inner surface of the piston ring 2 is designed for axial entrainment on the ring web 6 of the piston 3 as a cross-wedge-shaped or V-shaped annular groove 9, which has an upper conical surface 10 and a lower conical surface 11.
  • the piston ring 3 is made out of round, so that in the assembled state shown it is constantly pressed radially against the inner cylinder wall 12 of the cylinder 4 by its radial prestress and thus on the cylinder wall 12 during operation of the internal combustion engine rails are permanently sealed.
  • the left half section of the illustration in FIG. 1 shows the position of the piston ring 2 on the ring web 6 of the piston 3, which it assumes during the downward movement of the piston 3 in the direction of arrow 13 during the intake stroke of an internal combustion engine.
  • a negative pressure is created in the combustion chamber 14 of the cylinder 4 for drawing in a fuel / air mixture, so that the piston ring 2 with its lower conical surface 11 comes into sealing contact with the lower conical surface 8 of the ring land 6 , as shown in Fig. 1 in the left half of the picture.
  • the piston ring 2 lies with its outer circumferential surface 28 sealingly against the inner cylinder wall 12 of the cylinder 4, so that the combustion chamber 14 is separated in a sealing manner from the crankcase of the internal combustion engine during the intake stroke by the piston ring seal 1. Due to the cone angle ⁇ of the lower conical surfaces 8 and 11 with respect to the longitudinal piston center axis 29 or a parallel 30 to the longitudinal piston axis 29, which in the present exemplary embodiment is approximately 45 °, the radial pressure force of the piston ring 2 against the cylinder wall 12 is increased increasing vacuum at least slightly increased, whereby the tightness of the piston ring seal 1 is improved.
  • the piston ring 2 with its lateral surface 28 also lies sealingly against the inner cylinder wall 12 of the cylinder 4, so that the piston ring seal 1 also faces the combustion chamber 14 during these operating states, compression, combustion and ejection separates the crankcase of the internal combustion engine absolutely tight.
  • the cone angle ⁇ of the upper cone surfaces 7 and 10 with respect to the longitudinal piston center axis 30 or the parallel 31 in the present exemplary embodiment is approximately 45 ° and is therefore equal to the cone angle ⁇ of the lower cone surfaces 8, 11.
  • the Cone angles ⁇ and ß also assume different values, so that the radial force component increases or increases disproportionately with increasing vacuum in the intake cycle or with increasing compression or combustion pressure in the compression or combustion cycle, as a result of which the frictional forces occurring between the Mantle surface 28 of the piston ring 2 and of the cylinder wall 12 cylinder 4 can be influenced favorably.
  • the compression or compression stroke of the piston 3 is followed by the combustion stroke of the piston 3, in which the piston 3 moves downward again in the direction of the arrow 13 after the top dead center has been exceeded.
  • the high combustion pressure causes a further increase in the sealing radial force component with which the piston ring 2 bears against the cylinder wall 12, the combustion pressure acting on the one hand on the piston chamber 16 on the combustion chamber side and on the circumferential piston ring surface 17 of the piston ring 2 on the combustion chamber side.
  • the piston ring 2 becomes in the position shown in the right half of FIG. 1 due to the friction between the piston ring 2 and the cylinder wall 12, the discharge pressure in the combustion chamber 14 and also held in this position due to its inertia.
  • the piston ring 2 thus forms a common compression surface 18 with the piston 3 during the compression, combustion and exhaust stroke, consisting of the piston surface 16 and the piston ring surface 17, which has no circumferential gap in which fuel-air mixture, in particular during compression and the combustion cycle can penetrate. This ensures that the fuel-air mixture can only be located in the combustion chamber 14 and thus ensures that the fuel-air mixture is burned as completely as possible during the working cycle of the internal combustion engine. There is also no gap between the piston ring 2 and the cylinder wall 12 of the cylinder 4, so that even in this area no fuel-air mixture can accumulate during the compression stroke and incomplete combustion is also excluded here. 2 shows a further embodiment 1/1 of the piston ring seal 1, which has the same piston ring 2 as the piston ring seal 1.
  • the piston ring seal 1/1 has additional spring elements in the form of helical compression springs 19 which run in the ring web 6/1 of the piston 3/1 parallel to the upper conical surface 7 of the ring web 6/1 corresponding A receiving bores 27 are arranged.
  • the helical compression springs 19 press against the lower conical surface 11 of the piston ring 2, so that it is constantly held in its position shown in FIG. 2 by the spring force of the helical compression spring 19.
  • the provided helical compression springs 19 ensure that the piston ring 2 with its upper conical surface 10 rests permanently on the upper conical surface 7/1 of the ring land 6/1 of the piston 3/1, that is to say also during the intake stroke, and no change in the position of the piston ring 2 opposite or on the radial web 6/1 of the piston 3/1 during the entire operation of the internal combustion engine.
  • the provided helical compression springs 19 further ensure that the piston ring 2 can be made round, ie that it can be mounted on the piston 3/1 without its own radial prestressing or together with the latter in the cylinder 4, since the required radial prestressing is caused by the helical compression spring 19 is effected. This results in a considerably simpler manufacture of the piston ring 2, as a result of which the manufacturing costs for the piston ring 2 are reduced.
  • FIG. 3 shows a further exemplary embodiment 1/2 of the piston ring seal 1, which is also provided with a piston ring 2, which has the same structure as the piston ring 2 from FIG. 1.
  • the piston is designed on the combustion chamber side in such a way that its upper conical surface 7/2 and its ring web 6/2 continue upwards on the axial side of the combustion chamber, so that the compression surface 18/2 between the piston 3/2 and the piston ring 2 has a circumferential shoulder 20. Otherwise, the piston ring 2 is also held permanently by means of helical compression springs 19 in the position shown in FIG. 3 relative to the piston 3/2.
  • the piston ring seal 1/2 has no circumferential gap either between the piston ring 2 and the piston 3/2 or between the piston 3/2 and the inner cylinder wall 12 of the cylinder 4, so that there are also no gap spaces in which the fuel / air mixture can be stored.
  • optimum combustion of the fuel / air mixture in the corresponding combustion chamber 14/2 is ensured with this piston ring seal 1/2.
  • Fig. 4 shows a side view of the piston ring 2.
  • the piston ring 2 has a piston ring joint 21, which is double overlapping. Accordingly, the piston ring joint 21 is provided on one side with an impact groove 22 into which a shock spring 23 of the correspondingly encircling other end of the piston ring 2 projects.
  • the game between the shock spring 23 and the shock groove 22 has a total of about 0.01 mm, so that the piston ring butt 21 is absolutely gas-tight.
  • the butt joints 24 and 25 of the piston ring joint 21 are each arranged approximately in the middle of the upper conical surface 10 and the lower conical surface 11 of the piston ring 2.
  • the piston ring 2 can be mounted in a simple manner for mounting on the ring web 6, 6/1 or 6/2 of the pistons 3, 3/1 or 3/2 by spreading.
  • the shock spring 23 and the shock groove 22 are sharp in their shape, so that between the piston ring 2 and the ring web 6, 6/1, 6/2 or between the piston ring 2 and the cylinder wall 12 in the region of Piston ring butt 21 no gaps are formed and thus an absolute gas tightness can be achieved in this area of the piston ring 2.
  • Fig. 5 shows an embodiment 2/1 of the piston ring 1 in a bottom view.
  • the lower half of the piston ring 2/1 is provided with a plurality of spring tongues 26 arranged radially inward on the circumference.
  • the Federzun ⁇ gene 26 are each integral part of the piston ring 2/1.
  • These inwardly bent spring tongues 26, as can be seen from FIG. 6, are also bent towards the upper conical surface 10/1 of the piston ring 2/1, so that they are mounted on the lower conical surface 8, as shown in FIG 7 can be seen, resiliently and securely hold the piston ring 2/1 in the position shown in FIG. 7.
  • the spring tongues 26 are further adapted in their cross-section to the bending moment curve in such a way that they are subject to a constant bending stress over their entire length in the assembled, tensioned state, whereby a maximum degree of durability is achieved. This means that the spring tongues 26 are designed to taper in the circumferential direction towards their respective free end 31.
  • the piston ring 2/1 enables simple mounting of the piston ring 2/1 on the ring web 6 of the piston 3, since no separate spring elements elements, such as are present in the embodiments of FIGS. 2 and 3. Furthermore, the function of the piston ring 2/1 is identical to that of the piston ring 2 and, as can be seen in FIG. 7, also forms a common gapless compression surface 18 / with its upper piston ring surface 17/2 together with the piston surface 16 on the combustion chamber side. 2, so that even with this piston ring seal 1/3 the pollutant fan part of an internal combustion engine can be lowered considerably.
  • the piston ring 2/1 also has a piston ring joint 21/1, as can be seen from FIG. 5, which has the same structure as the piston ring joint 21 of the piston ring 2. It is of course also conceivable for the piston ring joint 21 or 21/1 to be formed simply overlapping, the overlapping components of which also have a play of approximately 0.01 mm and are also sharp-edged.
  • the inventive design of the piston ring seals 1 to 1/3 provides piston ring seals 1 to 1/3, which have no circumferential gaps on the combustion chamber side, in which fuel-air mixture can accumulate, which would then not be completely combustible in the combustion cycle.
  • the piston ring seal 1 to 1/3 according to the invention provides a piston ring seal 1 to 1/3, the design of which makes a considerable amount Reduction of the pollutants in the exhaust gas of an internal combustion engine can be achieved, while at the same time, due to the special type of guidance of the piston ring 2 or 2/1 on the correspondingly assigned ring web 6, 6/1 or 6/2, reliable guidance of the piston 3 er ⁇ reaches and thus a piston tilting is effectively prevented during operation.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

Dans les joints de segments de piston (1) de la technique antérieure, destinés aux moteurs à combustion interne, un segment (2) est disposé dans la zone terminale d'un piston (3), du côté de la chambre de combustion, et présente une surface intérieure (9) de forme conique qui agit conjointement avec un élément jointif annulaire (6) de forme conique correspondante. Le segment de piston (2) est en contact avec la paroi (12) d'un cylindre (4), dans lequel le piston est animé d'un mouvement axial. L'invention vise à améliorer les caractéristiques des gaz d'échappement d'un moteur à combustion interne. A cet effet, dans le cas du joint de segment de piston (1) décrit, la surface intérieure conique (9) du segment de piston (2) s'étend jusqu'à la surface supérieure (17) du segment de piston, du côté de la chambre de combustion, et l'élément jointif annulaire conique (6) du piston (3) s'étend avec sa surface conique supérieure (7) jusqu'à la surface supérieure (16) du piston, du côté de la chambre de combustion, de sorte que la surface (17) du segment de piston (2) forme une surface de compression (18) commune, sans espace vide, avec la surface (16) du piston (3).
EP95940986A 1994-11-17 1995-11-16 Joint de segment de piston Withdrawn EP0797743A1 (fr)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
DE4441004 1994-11-17
DE4441004 1994-11-17
DE4443186 1994-12-05
DE4443186 1994-12-05
DE4447290 1994-12-30
DE4447290 1994-12-30
PCT/EP1995/004499 WO1996016285A1 (fr) 1994-11-17 1995-11-16 Joint de segment de piston

Publications (1)

Publication Number Publication Date
EP0797743A1 true EP0797743A1 (fr) 1997-10-01

Family

ID=27206972

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95940986A Withdrawn EP0797743A1 (fr) 1994-11-17 1995-11-16 Joint de segment de piston

Country Status (3)

Country Link
EP (1) EP0797743A1 (fr)
JP (1) JPH10508931A (fr)
WO (1) WO1996016285A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5106376B2 (ja) * 2008-12-25 2012-12-26 Ｔｐｒ株式会社 内燃機関用ピストン装置
CN102384062B (zh) * 2010-08-30 2015-12-16 中国计量学院 活塞往复式压缩机的全无余隙机型的结构
KR101382049B1 (ko) * 2013-09-17 2014-04-04 이건호 유체이송용 실린더 펌프

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE408044A (fr) *
US1446658A (en) * 1921-08-13 1923-02-27 Harold Depew Piston ring
US2861852A (en) * 1957-07-18 1958-11-25 Olsen Arnt Olaf Piston and piston ring assembly
US3901131A (en) * 1969-04-14 1975-08-26 Ramsey Corp Anti-emissions compression piston ring
DE2933702C2 (de) * 1979-08-21 1981-09-17 Goetze Ag, 5093 Burscheid Kolbenring für insbesondere Brennkraftmaschinen
US5450783A (en) * 1994-03-10 1995-09-19 Dana Corporation Low emission piston ring

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9616285A1 *

Also Published As

Publication number Publication date
WO1996016285A1 (fr) 1996-05-30
JPH10508931A (ja) 1998-09-02

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