US3924979A - Rotary engine anti-spin oil seal - Google Patents

Rotary engine anti-spin oil seal Download PDF

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Publication number
US3924979A
US3924979A US424572A US42457273A US3924979A US 3924979 A US3924979 A US 3924979A US 424572 A US424572 A US 424572A US 42457273 A US42457273 A US 42457273A US 3924979 A US3924979 A US 3924979A
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United States
Prior art keywords
oil seal
seal groove
groove
rotor
facing
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Expired - Lifetime
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US424572A
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English (en)
Inventor
Dale P Rose
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Motors Liquidation Co
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General Motors Corp
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Publication date
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Priority to US424572A priority Critical patent/US3924979A/en
Publication of USB424572I5 publication Critical patent/USB424572I5/en
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    • 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
    • F01C19/12—Sealing arrangements in rotary-piston machines or engines for other than working fluid

Definitions

  • ABSTRACT A rotary engine anti-spin oil seal arrangement has a 52 US. Cl. 418/142 leek tab that is detaehably secured to and projects 51 1m. 01.
  • An object of the present invention is to provide a new and improved rotary engine anti-spin oil seal arrangement.
  • Another object is to provide a rotary engine anti-spin oil seal arrangement having a simple lock tab that readily secures to the oil seal and catches in a lock groove in an unsealed wall of the oil seal groove in the rotor to prevent the oil seal from turning in the oil seal groove while permitting normal oil seal movement.
  • Another object is to provide a rotary engine oil seal arrangement having a lock tab that is detachably secured to and projects from an unsealed side of the oil seal but does not interfere with an elastomeric seal mounted in a groove in a sealed side of the oil seal and catches on oil seal installation in a lock groove in the oppositely facing wall of the oil seal groove in the rotor to prevent the oil seal from spinning in the oil seal groove while permitting normal movement of the oil seal.
  • FIG. 1 is a longitudinal view with parts in section of a rotary engine having anti-spin oil seal arrangements constructed according to the present invention.
  • FIG. 2 is a view taken along the line 2-2 in FIG. 1 showing one rotor side.
  • FIG. 3 is an enlarged view of the anti-spin oil seal arrangements as shown in FIG. 2.
  • FIG. 4 is a view taken along the line 4-4 in FIG. 3.
  • FIG. 5 is a perspective view with parts broken away showing the lock tab arrangement.
  • FIG. 6 is a perspective view with parts broken away and exploded showing another embodiment of the lock tab.
  • FIG. 7 is a view similar to FIG. 6 showing another embodiment of the lock tab.
  • the present invention is for use in a rotary combustion engine of the planetary type shown in FIGS. 1 and 2.
  • the engine comprises a housing 10 which in a single rotor arrangement, as shown, has basically three parts;
  • a rotor housing 12 having an inwardly facing inner peripheral wall 14 and a pair of side housings 16 and 18 having parallel, oppositely facing, spaced inner side walls 20 and 22, respectively.
  • the housing parts are secured together by bolts, not shown, and the inner housing walls 14, 20 and 22 cooperatively provide a cavity 24.
  • the peripheral wall 14 is a two-lobe curve with a center line indicated at 26.
  • a crankshaft 28 extends through the cavity and is rotatably supported in sleeve bearings 30 and 32 which are secured in collars 34 and 36 that are bolted to the side housings l6 and 18, as shown in FIG.
  • crankshaft axis being coincident with the center line 26, parallel to the peripheral wall 14 and at right angles to the side "walls 20 and 22.
  • the crankshaft 28 is provided in cavity 24 with an eccentric 38.
  • a three-lobe rotor 40 has a hub 41 having a sleeve bearing 42 secured therein which is received on the eccentric 38 so that the rotor is thereby supported in cavity 24 for rotation about the eccentric s center line 44 which is thus the rotors axis.
  • the rotor 40 has the general shape of an arcuate sided triangle with two parallel sides 46 and 48 at right angles to the rotor axis which face and run close to the side walls 20 and 22, respectively, and an outer peripheral wall having three arcuate outer faces 50 which face the peripheral wall 14 and cooperate therewith and with the side walls 20 and 22 to define three variable volume working chambers 52. Sealing of these chambers is effected by gas sealing means comprising three apex seals 54 which are each mounted in an axially extending groove or slot at each apex or corner of the rotor 40 and extend the width thereof. Three arcuate side seals 56 are mounted in accommodating grooves in each rotor side and extend adjacent the rotor faces between two of the apex seals 54.
  • Three cylindrical corner seals 58 are mounted in cylindrical blind bores in each rotor side contiguous with the apex seal slots with each comer seal having a slot receiving one end of an apex seal and providing sealing, between the ends of two side seals and one apex seal as shown in FIG. 2.
  • the apex seals 54 are spring biased to engage the peripheral wall 14 and both the side seals 56 and the corner seals 58 are spring biased toengage the respective side walls 20 and 22 with the complete gas seal arrangement acting to seal the working chambers.
  • each of the working chambers 52 sequentially expands and contracts between minimum and maximum volume twice during each revolution while the rotor apexes closely follow the peripheral wall by forcing the rotor to rotate at one-third the speed of the crankshaft.
  • gearing comprising an internal tooth gear 62 which is formed integral with the righthand side 48 of the rotor with its center on the rotor axis.
  • the gear 62 meshes 'with an external tooth annular gear 64 which is freely received about and is concentric with the crankshaft 28 and is made stationary by being formed integral with the left-hand end of the right-hand collar 36 as shown in FIG. 1.
  • the gear 62 has one and one-half times the number of teeth as the gear 64 to provide the required speed ratio of 3:1 between the crankshaft and the rotor.
  • Intake passage 66 extends through the engine housing and opens to the cavity through either the peripheral wall 14 or through aligned side wall ports 67, only one of which is shown, or through a combination thereof with such porting being located on the leading side of cusp 68 of the peripheral wall relative to the direction of rotor rotation indicated by the arrow in FIG. 2.
  • the rotor sides uncover the intake ports to the chambers as they are expanding in the intake phase to draw in the combustible mixture and then closes this intake opening to them when they are contracting to compress the mixture in the following compression phase.
  • a single channel or recess 69 is provided in the center of each chamber face of the rotor so that when each rotor face is at or near its top-dead-center position with its center opposite the peripheral walls other cusp 70, the associated chamber is not then divided by this cusp.
  • a spark plug 72 is mounted in the rotor housing 12 adjacent the cusp 70 with its electrodes exposed to the passing working chambers and is supplied with voltage from a suitable ignition system, not shown, at the proper time at or near top-dead-center to initiate combustion at the end of the compression phase.
  • the peripheral wall 14 takes the reaction forcing the rotor to continue rotating while the gas is expanding in the expansion or power phase.
  • the leading apex seal 54 of the working chambers eventually traverses an exhaust passage 74 in the rotor housing on the trailing side of the cusp 68 whereby the exhaust products are then expelled in the exhaust phase to complete the cycle.
  • the rotor 40 has a hollow interior and is webbed for rigidity and a radial oil passage 94 in the crankshaft 28 delivers oil from the passage 86 to lubricate the gears 62 and 64 and also to the rotors interior for cooling of the rotor with the oil carrying the heat from the rotor by passing to annular cavities 96 and 98 in the respective side walls 20 and 22 that are connected by passages, not shown, to drain to the sump.
  • each side of the rotor inner and outer circular oil seals 100 and 102 of metal that are located radially inwardly of the side seals 56 in accommodating axially outwardly facing circular grooves 104 and 106, respectively, that are centered on the rotor axis 44. As best shown in FIG.
  • the oil seals 100 and 102 in each rotor side are biased to engage the oppositely facing housing side wall to prevent the oil supplied for lubrication and cooling from reaching the radially outwardly located gas seals by split annular wave springs 108 and 1 that engage on one spring side with the oil seal grooves planar bottoms 112 and 114 and on the other spring side with the oil seals planar backsides 116 and 118, respectively.
  • sealing is provided between the oil seals 100 and 102 and the rotor by elastomeric 0- rings 120 and 122 which are mounted in annular grooves 124 and 126 in the radially outwardly and inwardly facing sides 128 and 130 of the respective oil seals 100 and 102, these grooves being rectangular in cross-section.
  • the O-ring grooove 124 in the inner oil seal 100 faces radially outwardly with the O-ring 120 engaging the oppositely radially. facing wall 132 of the oil seal groove 104.
  • the O-ring groove 126 in the outer oil seal 102 faces radially inwardly with the O-ring 122 engaging the oppositely radially facing wall 134 of the oil seal groove 106.
  • the O-rings and 122 seal the respective radial clearances 136 and 138 between the oil seals 100 and 102 and the oil seal groove walls 132 and 134 while the radial clearances 140 and 142 between the other radially facing oil seal sides 144 and 146 and oil seal groove walls 148 and 150 are left open.
  • each of the lock tabs 156 is formed of wire and as fabricated has a simple U- shape, as shown in broken line in FIG. 5, with legs 158 that are then parallel to permit assembly.
  • radial holes 160 are drilled through the unsealed radially inwardly facing side 144 with these holes positioned close to the rearward corner of the O-ring groove 124 and being angularly spaced to receive the lock tab legs 158.
  • the legs 158 of the lock tab 156 are inserted from the unsealed side 144 of the oil seal through the holes 160 with the bight 162 of the tab projecting radially inwardly of the oil seal 100 on the unsealed side.
  • the legs 158 are then bent in opposite angular directions to fit along the rearward corner of groove 124. This positively secures the lock tab 156 to the oil seal wherefter the O-ring 120 may be inserted in the O-ring groove 124 in the normal manner since the lock tab legs 158 are in locations so as not to interfere therewith.
  • the oil seal 100 is then inserted in the oil seal groove 104 in the rotor with the bight 162 of the lock tab 156 fitting in the lock groove 152.
  • the lock groove 152 captures the bight 162 of the lock tab 156 to prevent the oil seal 100 from spinning in the oil seal groove 104 but because of the lock groove alignment with the normal direction of seal movement permits the bight 162 to move therealong so that the oil seal 100 remains free to move axially to maintain sealing engagement with the housing side wall. Since the lock tab 156 is located in a most rearward location, there is no reasonable possibility that it will leave the lock groove during the life of the oil seal. Thus,-the lock tab 156 does not interfere with the normal sealing action of either the O-ring 120 or the oil seal 100. Similar locking without seal interference is provided for the outer oil seal 102 as shown in FIGS.
  • the unsealed side of the outer oil seal 102 is the radially outwardly facing side 146 and that the lock tab holes in the oil seal are through this side and that the outer lock tab 156 projects from this oil seal side to engage the lock groove 154 in the unsealed wall 150 of the outer oil seal groove 106.
  • FIG. 6 wherein structure similar to that previously described is identified by the same numbers only primed and substantially different structure is described by different numbers, there is shown another embodiment of the lock tab which is also of wire but does not require any further forming for retention on the oil seal.
  • the lock tab 156 has a fabricated -shaped and instead of radially drilled holes in the oil seal there is provided a single slot 160' through the unsealed side 144 of the oil seal that is in the same location as the drilled holes with its width slightly larger than that of the wire diameter and a length measured in the angular direction that is smaller than the free or unsprung dimension A measured across the widest portion of the bight 162'.
  • the preformed legs 158' are compressed in angularly opposite directions to reduce the size of the bight 162 sufficiently to permit its entry into the slot 160' from the O-ring groove side whereafter on release of this assembly force the lock tab is held by the added oppositely facing detent bends 164 which catch the opposite ends 166 of the slot 160'.
  • the bight 162 operates in the lock groove in the oil seal groove in the rotor as previously described to prevent oil seal spin while not interfering with the sealing action.
  • FIG. 7 there is shown another embodiment of the lock tab which like the FIG. 6 embodiment does not require any additional forming for retention on the oil seal and wherein similar structure is identified by the same numbers only double primed and substantially different structure is identified by different numbers.
  • the lock tab 156" is stamped from sheet metal and has a rounded head 162" which fits through the slot 160" in the unsealed side 144" of the oil seal and also has a single transversely extending leg 158" which is of longer dimension than the length of the lock slot 166" that is fully received in and along the one wall of the O-ring groove.
  • the head 162 has locking ears 168 that project out of the normal plane of i the tab and are deflected into this plane to permit insertion of the head and ears through the slot 166 whereafter the ears spring back to their nonnal angle to prevent removal of the lock tab and together with the leg 158" positively hold the lock tab on the oil seal.
  • the head 162" operates in the lock groove in the oil seal groove in the rotor as previously described to prevent oil seal spin while permitting normal oil seal action.
  • a rotary engine having a housing with an inwardly facing peripheral wall and oppositely facing inner side walls cooperatively defining a cavity, a crankshaft rotatably supported in said housing, said crankshaft having an eccentric located in said cavity, a rotor rotatably mounted on said eccentric in said cavity, said rotor having sides facing said side walls and peripheral faces facing said peripheral wall defining a plurality of chambers that are spaced about and move with said rotor while varying in volume as said rotor rotates, a circular groove to sealingly engage the opposite housing side wall, an elastomeric seal groove in one of said radially facing sides of said oil seal, said elastomeric seal groove having a radially facing bottom opposite one of the walls of said oil seal groove and radially extending oppositely facing walls, an elastomeric seal mounted in said elastomeric seal groove in said oil seal and engaging the bottom of said elastomeric seal groove and the oppositely radially facing said one wall of said oil seal groove to provide sealing between said oil
  • a rotary engine having a housing with an inwardly facing peripheral wall and oppositely facing inner side walls cooperatively defining ,a cavity, a crankshaft rotatably supported in said housing, said crankshaft having an eccentric located in said cavity, a rotor rotatably mounted on said eccentric in said cavity, said rotor having sides facing said side walls and peripheral faces groove bottom and said oil seal backside for biasing said oil seal to normally move axially in said oil seal groove to sealingly engage the opposite housing side wall, an elastomeric seal groove in one of said radially facing sides of said oil seal, said elastomeric seal groove having a radially facing bottom opposite one of the walls of said oil seal groove and radially extending oppositely facing walls, an elastomeric seal mounted in said elastomeric seal groove in said oil seal and engaging the bottom of said elastomeric seal groove and the oppositely radially facing said one wall of said oil seal groove to provide sealing between said oil seal and said rotor while said oil seal sealingly engages the housing
  • a rotary engine having a housing with an inwardly facing peripheral wall and oppositely facing inner side walls cooperatively defining a cavity, a crankshaft rotatably supported in said housing, said crankshaft having an eccentric located in said cavity, a rotor rotatably mounted on said eccentric in said cavity, said rotor having sides facing said side walls and peripheral faces facing said peripheral wall defining a plurality of chambers that are spaced about and move with said rotor while varying in volume as said rotor rotates, a circular oil seal groove in each side of said rotor with its center on the rotor axis, a circular oil seal in each said oil seal groove axially movable to sealingly engage the opposing side wall, said oil seal having a backside and oppositely radially facing sides, said oil seal groove having a bottom and oppositely radially facing walls, a wave spring mounted in said oil seal groove engaging said groove bottom and said oil seal backside for biasing said oil seal to normally move axially in said oil seal groove to sealingly engage the
  • a rotary engine having a housing with an inwardly facing peripheral wall and oppositely facing inner side walls cooperatively defining a cavity, a crankshaft rotatably supported in said housing, said crankshaft having an eccentric located in said cavity, a rotor rotatably mounted on said eccentric in said cavity, said rotor having sides facing said side walls and peripheral faces facing said peripheral wall defining a plurality of chambers that are spaced about and move with said rotor while varying in volume as said rotor rotates, a circular oil seal groove in each side of said rotor with its center on the rotor axis, a circular oil seal in each said oil seal groove axially movable to sealingly engage the opposing side wall, said oil seal having a backside and oppositely radially facing sides, said oil seal groove having a bottom and oppositely radially facing walls, a wave spring mounted in said oil seal groove engaging said groove bottom and said oil seal backside for biasing said oil seal to normally move axially in said oil seal groove to sealingly engage the

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US424572A 1973-12-13 1973-12-13 Rotary engine anti-spin oil seal Expired - Lifetime US3924979A (en)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3985478A (en) * 1973-11-07 1976-10-12 General Motors Corporation Rotary engine anti-spin oil seal
US4102617A (en) * 1976-11-12 1978-07-25 Toyota Jidosha Kogyo Kabushiki Kaisha Oil seal means in a rotary piston engine
US4106780A (en) * 1977-10-26 1978-08-15 Ingersoll-Rand Company Seal carrier for rotary piston engine
US6092812A (en) * 1996-12-19 2000-07-25 Robert Bosch Gmbh Water-tight plastic component
US8985085B2 (en) 2011-07-28 2015-03-24 Pratt & Whitney Canada Corp. Oil seal arrangement for rotary internal combustion engine
US9366138B2 (en) 2011-07-28 2016-06-14 Pratt & Whitney Canada Corp. Rotary internal combustion engine with phasing gear

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE18776E (en) * 1933-03-28 By elsie c
FR860740A (fr) * 1939-07-06 1941-01-22 Segment élastique pour piston de moteur
US3193188A (en) * 1963-04-11 1965-07-06 Curtiss Wright Corp Rotor and seal construction for rotary mechanisms
DE1233198B (de) * 1962-11-24 1967-01-26 Daimler Benz Ag Mehrfach-Innendichtung fuer Rotationskolben-Brennkraftmaschinen
US3575541A (en) * 1968-12-11 1971-04-20 Yanmar Diesel Engine Co Oil sealing unit in rotary piston engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE18776E (en) * 1933-03-28 By elsie c
FR860740A (fr) * 1939-07-06 1941-01-22 Segment élastique pour piston de moteur
DE1233198B (de) * 1962-11-24 1967-01-26 Daimler Benz Ag Mehrfach-Innendichtung fuer Rotationskolben-Brennkraftmaschinen
US3193188A (en) * 1963-04-11 1965-07-06 Curtiss Wright Corp Rotor and seal construction for rotary mechanisms
US3575541A (en) * 1968-12-11 1971-04-20 Yanmar Diesel Engine Co Oil sealing unit in rotary piston engine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3985478A (en) * 1973-11-07 1976-10-12 General Motors Corporation Rotary engine anti-spin oil seal
US4102617A (en) * 1976-11-12 1978-07-25 Toyota Jidosha Kogyo Kabushiki Kaisha Oil seal means in a rotary piston engine
US4106780A (en) * 1977-10-26 1978-08-15 Ingersoll-Rand Company Seal carrier for rotary piston engine
US6092812A (en) * 1996-12-19 2000-07-25 Robert Bosch Gmbh Water-tight plastic component
US8985085B2 (en) 2011-07-28 2015-03-24 Pratt & Whitney Canada Corp. Oil seal arrangement for rotary internal combustion engine
US9366138B2 (en) 2011-07-28 2016-06-14 Pratt & Whitney Canada Corp. Rotary internal combustion engine with phasing gear

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