US3249094A - Lubricating sealing means for rotary combustion engines - Google Patents

Lubricating sealing means for rotary combustion engines Download PDF

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Publication number
US3249094A
US3249094A US315280A US31528063A US3249094A US 3249094 A US3249094 A US 3249094A US 315280 A US315280 A US 315280A US 31528063 A US31528063 A US 31528063A US 3249094 A US3249094 A US 3249094A
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US
United States
Prior art keywords
piston
shaft
housing
sealing
disc
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.)
Expired - Lifetime
Application number
US315280A
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English (en)
Inventor
Hoppner Ernst
Lechler Rolf
Hoffmann Gunter
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.)
Wankel GmbH
Audi AG
Original Assignee
Wankel GmbH
NSU Motorenwerke AG
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 Wankel GmbH, NSU Motorenwerke AG filed Critical Wankel GmbH
Application granted granted Critical
Publication of US3249094A publication Critical patent/US3249094A/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/10—Sealings for working fluids between radially and axially movable parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F02B2053/005—Wankel engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2730/00—Internal-combustion engines with pistons rotating or oscillating with relation to the housing
    • F02B2730/01—Internal-combustion engines with pistons rotating or oscillating with relation to the housing with one or more pistons in the form of a disk or rotor rotating with relation to the housing; with annular working chamber
    • F02B2730/018—Internal-combustion engines with pistons rotating or oscillating with relation to the housing with one or more pistons in the form of a disk or rotor rotating with relation to the housing; with annular working chamber with piston rotating around an axis passing through the gravity centre, this piston or the housing rotating at the same time around an axis parallel to the first axis
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • This invention relates to internal combustion engines, in particular to those of the rotary piston type, and is directed to improved sealing means between relatively moving parts of such engines.
  • engines of this type comprise an outer body formed by a peripheral wall interconnected by a pair of parallel end walls thereby defining a cavity whose peripheral shape preferably is basically an epitrochoid.
  • a rotatably mounted rotor is supported for eccentric movement on a shaft within the cavity "and has a plurality of circumferentially-spaced apex portions with radially movable seal strips mounted therein for sealing engagement with the inner surface of the peripheral wall, thereby forming Working chambers which upon relative rotation of the outer body and rotor vary in volume.
  • An in take port is provided for admitting a fuel-air mixture to the combustion zone of said engine, and an exhaust port is provided for expelling the burnt gases.
  • a lubrication'system for the engine shaft and bearings generally includes means for supplying lubricating oil also to the interior of the. rotor for cooling purposes.
  • this oil-seal ring which is in direct heatconducting relation to the piston, often includes in part a non-metallic rubber-like material which deteriorates gradually at piston temperatures, thereby limiting the useful life of such rings.
  • a principal object of this invention therefore is to provide new and improved lubricant sealing means for a rotary combustion engine of the character described, wherein an oil sealing device is interposed between the engine shaft structure and the piston for preventing leakage of oil from the transmission area past the piston into the operating chambers.
  • a further object of the invention is to provide in a preferred form new and improved sealing means wherein oil sealing ring structure is carried by and rotatable with the shaft structure for directly engaging the piston and avoiding the sealing difficulties previously referred to.
  • the present invention provides primary and secondary oil sealing means, both preferably carried by the conventional shaft eccentric.
  • the primary sealing means engages directly the piston side walls for sealing the shaft, transmission and bearing areas containing the pressurized lubricant with respect to the piston, and the secondary sealing means likewise carried by the eccentric (or cam) makes a shaft-housing seal for the comparatively low-pressure exhaust lubricant, thereby preventing leakage of lubricant along the housing side walls to the piston along a path lay-passing the shaft piston seal.
  • FIGURE 1 is a simplified sectional view of a rotary combustion engine of the type to which the present invention is applicable;
  • FIGURE 2 is a detailed sectional. view of the engine taken generally along the line 2-2 of FIGURE 1 showing application of the invention thereto;
  • FIGURE 2A is an enlarged detail view of the piston seal shown in FIGURE 2;
  • FIGURE 3 is a sectional view taken along the line 3-3 of FIGURE 2 showing the piston drive and shaft eccentric structure of the engine;
  • FIGURES 4, 5 and 6, 7 are separate detail views of the seal discs of FIGURE 2 that are mounted on opposite sides of the engine shaft eccentric;
  • FIGURES 8, 9 and 10 are detail views in section showing alternative forms of the piston seal.
  • FIGURES l and 2 there is shown a rotary combustion engine having an outer body or housing generally designated at 1 composed of a pair of end walls 3 and 4 interconnected by a peripheral wall 2.
  • the housing defines a cavity therein having a transverse axis M1.
  • the profile of the inner wall 2 is basically a two-lobed epitrochoid.
  • a shaft 6 is rotatably mounted in the housing co-axial with the axis M1 and has an eccentric portion 7 formed thereon.
  • a rotor 8 is rotatably mounted on the eccentric and has three circumferentially spaced apex portions 12, FIG- URES l and 2, which are in sealing cooperation with the inner surface 2 to form a plurality of working chambers 5 which upon relative rotation of the wall 2 and rotor 8 vary in volume.
  • Seal strips 12 as indicated are mounted in each apex portion and extend from one end face of the rotor to the other end face, FIGURE 2, for continuous sealing engagement with the inner surface 2, thereby sealing the working chambers 5.
  • End face seals 3 and 4' are also provided in each end or side face of the rotor and are in sealing engagement with the housing side walls 3 and 4 at surfaces 311 and 4a respectively, to prevent leakage of the gases from the working chambers 5 past the rotor in known manner.
  • a suitable bearing 9 is supported in the rotor 8 for rotatively supporting the rotor on the eccentric 7.
  • Suitable bearings 6a and 6b are also mounted in the end walls 3 and 4. as shown in FIGURE 2 for supporting the rotating shaft 6 in the housing.
  • the rotor (piston) drive connection with the shaft comprises an externally-toothed gear or pinion 10 that is secured to the shaft journal box at the wall 4 in meshing engagement with an internally-toothed gear 11 which constitutes an end-portion of the rotor inner bearing ring 11'.
  • the gears and 11 serve to r-otatively position the rotor with respect to the epitrochoidal surface of the peripheral wall 2.
  • FIG. 1 illustrating a two-lobed epitrochoid and a threelobed rotor
  • the ratio of rotation of the eccentric 7 and its shaft 6 with respect to the rotor is 3:1, i.e., for each rotation of the rotor about its axis M2, which corresponds to the center of the eccentric 7, the eccentric and shaft 6 rotate three times around the shaft axis M1.
  • the eccentricity E of the cam 7 represents the piston throw or stroke.
  • the lubrication system for the essential bearings and gears including the main shaft bearings 6a and 6b, the piston-eccentric bearings 9 and the piston position gearing 10-11 comprises interconnecting passages in the housing, shaft structure and piston hereinafter described through which a lubricating medium referred to as oil, is circulated.
  • the oil is applied as indicated by direction arrows so as both to lubricate the main shaft bearings and the transmission and drive parts, and also to cool the interior of the piston.
  • the main oil seal is made essentially between the shaft eccentric and the piston itself, rather than between the engine side walls and piston ac cording to prior practice as explained above.
  • the shaft eccentric 7 there is secured to the shaft eccentric 7 at least one seal-carrying member 14 or 15, as the case may be, located between one side of the eccentric and the corresponding housing side wall.
  • the member 14 (or 15) may be of disc-like form having its center coincident with the center of the eccentric 7 which also defines the axis of rotation M2 of the piston. As shown in FIGURE 3, the disc 15 is cut away at 21 to form a crescent for rotation clearance at the piston internal ring gear 11, companion fixed gear 10 and shaft 6.
  • a single disc may be used for sealing purposes at one side of the piston in accordance with the invention (the piston in such case having a conventional ring seal at its opposite side and being axially biased toward that side of the housing)
  • a preferred construction includes two discs 14 and 15 secured as by bolts to opposite sides of the eccentric, FIGURES 2 and 3, for rotation with-the shaft 6.
  • the disc peripheries are located respectively opposite a recess wall 18 formed at each side of the piston, FIGS. 2 and 2A.
  • This ring is composed of a suitable metal and has a generally U-shape cross-section. It is retained within the outer part of the disc 14 by a transverse flange thereof 14', so as to be concentric of the piston axis M2 and movable axially, -i.e., toward and away from the piston side wall 80.
  • the ring is resiliently biased toward the piston wall by an annular spring 17 positioned between the inner side of the disc and the ring as shown.
  • the ring may have an annular shoulder on its inner periphery at the disc side for retaining the spring.
  • a fluid-tight seal between the ring 16 and disc flange 14 is provided by an O-ring 16a of rubber-like material enclosed under compression within the U of the ring. Accordingly, the ring 16 which is biased laterally to make annular wiping engagement with the adjacent piston side wall 80 completes a seal between that piston wall surface 8a and the shaft eccentric and disc structure.
  • the normally oil-containing passages and spaces referred to above for lubricating and cooling purposes are formed in part by the sealing discs 14 and 15.
  • the oil enters the housing by a passage a formed inthe end wall 4 and communicates with the gearing 10-11 through an annular passage b formed in the corresponding main bearing housing.
  • the cut-away part of the disc 15 at 21 admits oil from passage b to all the gearing 1041 during rotation of the piston around the fixed gear 10. From passage b the oil flows through radiating passages c formed in the disc 15 to the piston-eccentric bearings 9, and through passage 0! in the ring gear and piston into the hollow piston cooling pas-' sage e.
  • the disc 15 is provided with a circular flange or hub portion 22a, FIGURES 2 and 5, that makes an oil seal at 22b with the housing end wall 4 as shown, thereby sealing the piston at its side 8b from oil in the annular passage b.
  • the oil outlet from the piston cavity e includes another passage 1 in the piston and ring gear which communicates with a generally circular space g formed in part between a crescent-shape portion 14' of the disc 14, FIGURES 2, 6 and 7, and the surrounding wall of the piston at its inner-periphery.
  • This space in turn opens into the cylindrical hub extension 22 of the disc which extends over a smaller diameter hub 3' formed on the bearing housing and constituting part of the engine side wall.
  • the space therebetween defines an annular passage h leading to the oil exhaust port k.
  • the hub which is rotatable within the end wall 3 is provided, as in the case of the hub 22 of disc 15, with an oil seal, such as spiral grooves 23 formed in the outer surface of the hub.
  • FIGS 8, 9 and 10 Alternative forms of seals used according to the invention are shown by FIGURES 8, 9 and 10.
  • a resilient seal ring 16 is carried by disc 14 for example, within an annular groove 16" and is biased by suitable spring means axially outward rather than inward, to make the piston seal.
  • a metal companion ring or annulus 25 overlapping and surround ing the disc periphery is mounted on the piston itself to form an extension of its side wall along the housing wall.
  • the ring has a radially extending flange 26 with a re-entrant edge 26' that fits within 2.
  • corresponding groove in the disc 14 to form a supplemental labyrinth-type seal.
  • the annular clearance gap 27 between the disc 14 and ring- 25 is in communication with the oilcooling space e in the piston and slants radially outward as shown. Accordingly, oil from the passage 2 tending to enter the clearance gap is flung back into the piston cavity by centrifugal force due to the higher rotative speed of the disc 14. Oil from the piston space e is thereby prevented from leakage past the disc into the piston-housing clearance and so into the engine operating chambers 5.
  • the sealing ring 16' of FIGURE 8 is dispensed with and in lieu thereof a so-called gap-seal is used.
  • the disc 14 and piston ring 25 have close tolerance clearance surfaces that may have a generally Z-shape form as shown.
  • the radially extending part 28 of the clearance gap has a minimum length H to prevent leakage of oil from the piston cavity e past the disc. This length depends on engine design factors affecting the centrifugal force available to force back oil into the piston cavity, including the maximum oil level in the piston cavity, the spacing of the radially extending outer end of the gap from the eccentric (disc) axis of rotation M2, and the piston throw E.
  • a further consideration is that oil entering the radial passage 28 be given to maximum extent the rotative speed of the disc. To this end, the aforesaid tolerance should be as small as possible and the gap surface area of the higher speed disc be made rough and that of the lower speed piston ring 25 be made smooth.
  • FIGURE shows a variation of the gap-seal wherein labyrinth sealing between the disc 14 and piston at 29 is used.
  • the piston ring and the disc 14 overlap radially and have a staggered tongue and groove mating configuration to form a labyrinth along the clearance gap.
  • the discs 14 and 15 though preferably concentric with the piston axis of rota.- tion M2, may have a slight eccentricity with resepct to this axis where the seal of FIGURE 2, for example is used. This eccentricity can be advantageous for widening the seal-wiped area of the piston wall where the seal tends to abrade and wear a groove in the piston.
  • the shaftsecured means is a rigid member, generally in a plane parallel to a side wall of the piston, said member and a generally similar member being rotatable with the shaft and extending along opposite side walls respectively of the piston, each member having means for retaining its respective sealing structure for engaging a corresponding side wall of the piston.
  • shaftsecured means also has a hub portion surrounding the shaft for engaging in sealing relation the engine housing side wall for sealing the lubricant within that part of the housing enclosing the shaft.
  • sealing structure comprises a sealing ring mounted in said shaftsecured means and biased in a direction parallel to the shaft axis into sealing engagement with a side wall of the piston.
  • shaftsecured means is a disc concentric with the piston axis of rotation and rotatable with the shaft, said disc having a peripheral flange portion formed to retain said sealing ring in sealing. contact with the piston.
  • sealing ring is composed of metal and a resilient non-metallic ring is mounted between the metal ring and shaft-secured means for sealing the engaging surfaces thereof.
  • the sealing structure constitutes a split seal ring forming a narrow clearance slot extending radially with respect to the piston axis whereby centrifugal force due to rotation of said shaft-secured means tends to prevent passage of lubricant through said slot toward the shaft.
  • the sealing structure comprises an annular metal sealing annulus forming an extension of the piston side wall
  • the shaft-secured means is a disc, the peripheral portion of said disc being surrounded in close tolerance by said annulus to form a gap-seal and the disc and annulus surfaces defining a generally Z-shape gap having a radially extending portion through which leakage of oil toward the shaft is opposed by centrifugal force incident to rotation of said disc.
  • sealing structure constitutes a split-seal ring, one part of which is attached to a piston edge at the housing side wall, the other part being attached to the shaft-secured means, the clearance gap between said parts defining a close tolerance labyrinth.
  • an internal combustion engine of the rotary piston type having a housing, a piston mounted for eccentric rotation within said housing successively to form with said housing walls variable-volume operating chambers, a rotatable power output shaft mounted in said housing, and transmission drive means including an eccentric between said piston and shaft provided with continuous lubrication, a member secured to said eccentric for rotation therewith, and sealing means interposed axially between a peripheral part of said member and a side wall of the piston and mounted in one of them to preclude leakage of lubricant from the shaft and transmission areas past the piston at said side wall into said operating chambers.
  • the eccentric-secured member is a disc secured to the eccentric at one side thereof and extends adjacent to a piston side wall
  • the sealing means constitutes a ring-type seal surrounding the shaft concentrically of the piston axis of rotation and mounted between the respective side walls of the disc and piston to be sealed for making, together with said disc, an axial seal between the shaft and the aforesaid piston side wall.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Details Of Gearings (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Valve Device For Special Equipments (AREA)
  • Sealing Devices (AREA)
US315280A 1962-10-13 1963-10-10 Lubricating sealing means for rotary combustion engines Expired - Lifetime US3249094A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DEN22209A DE1187854B (de) 1962-10-13 1962-10-13 Kreiskolbenmaschine, insbesondere -Brennkraftmaschine in Trochoidenbauart

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US3249094A true US3249094A (en) 1966-05-03

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DE (1) DE1187854B (de)
GB (1) GB1017568A (de)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3323713A (en) * 1964-12-10 1967-06-06 Nsu Motorenwerke Ag Sealing arrangement for rotary mechanisms
US3323712A (en) * 1965-12-11 1967-06-06 Nsu Motorenwerke Ag Rotary internal combustion engine
US3333763A (en) * 1966-02-02 1967-08-01 Nsu Motorenwerke Ag Sealing arrangement for rotary engines
US3369740A (en) * 1966-05-04 1968-02-20 Kloeckner Humboldt Deutz Ag Rotary piston internal combustion engine, especially circular piston internal combustion engine
US3415444A (en) * 1965-12-15 1968-12-10 Goetzewerke Oil seal for rotary piston internal-combustion engines
US3590790A (en) * 1968-09-07 1971-07-06 Kloeckner Humboldt Deutz Ag Contact-free oil seal for rotary piston internal combustion engines
US4830591A (en) * 1987-05-26 1989-05-16 Wankel Gmbh Lubrication system for a rotary-piston internal combustion engine
US5049049A (en) * 1990-05-18 1991-09-17 Wankel Gmbh Rotary piston internal combustion engine
US20050186103A1 (en) * 2004-02-20 2005-08-25 Wankel Super Tec Gmbh Rotary combustion engine with device for conveying lubricating oil
WO2006048212A3 (de) * 2004-10-29 2006-06-29 Herbert Jung Pumpe, insbesondere dickstoffpumpe

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4003675A1 (de) * 1990-02-07 1991-08-08 Wankel Gmbh Rotationskolbenbrennkraftmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3323713A (en) * 1964-12-10 1967-06-06 Nsu Motorenwerke Ag Sealing arrangement for rotary mechanisms
US3323712A (en) * 1965-12-11 1967-06-06 Nsu Motorenwerke Ag Rotary internal combustion engine
US3415444A (en) * 1965-12-15 1968-12-10 Goetzewerke Oil seal for rotary piston internal-combustion engines
US3333763A (en) * 1966-02-02 1967-08-01 Nsu Motorenwerke Ag Sealing arrangement for rotary engines
US3369740A (en) * 1966-05-04 1968-02-20 Kloeckner Humboldt Deutz Ag Rotary piston internal combustion engine, especially circular piston internal combustion engine
US3590790A (en) * 1968-09-07 1971-07-06 Kloeckner Humboldt Deutz Ag Contact-free oil seal for rotary piston internal combustion engines
US4830591A (en) * 1987-05-26 1989-05-16 Wankel Gmbh Lubrication system for a rotary-piston internal combustion engine
US5049049A (en) * 1990-05-18 1991-09-17 Wankel Gmbh Rotary piston internal combustion engine
US20050186103A1 (en) * 2004-02-20 2005-08-25 Wankel Super Tec Gmbh Rotary combustion engine with device for conveying lubricating oil
US7234924B2 (en) * 2004-02-20 2007-06-26 Wankel Super Tec Gmbh Rotary combustion engine with device for conveying lubricating oil
WO2006048212A3 (de) * 2004-10-29 2006-06-29 Herbert Jung Pumpe, insbesondere dickstoffpumpe
EA010914B1 (ru) * 2004-10-29 2008-12-30 Херберт Юнг Насос, в частности шламовый насос
DE102004052928B4 (de) * 2004-10-29 2009-06-04 Herbert Jung Pumpe, insbesondere Dickstoffpumpe
CN101107447B (zh) * 2004-10-29 2010-06-02 赫伯特·琼 泵，尤其是泥浆泵
US8192183B2 (en) 2004-10-29 2012-06-05 Herbert Jung Prismatic pump, especially slurry pump
KR101190336B1 (ko) 2004-10-29 2012-10-11 헤르베르트 융 슬러리 펌프

Also Published As

Publication number Publication date
DE1187854B (de) 1965-02-25
GB1017568A (en) 1966-01-19

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