US3816041A - Oil seal for rotary mechanism - Google Patents

Oil seal for rotary mechanism Download PDF

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Publication number
US3816041A
US3816041A US00321235A US32123573A US3816041A US 3816041 A US3816041 A US 3816041A US 00321235 A US00321235 A US 00321235A US 32123573 A US32123573 A US 32123573A US 3816041 A US3816041 A US 3816041A
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US
United States
Prior art keywords
oil seal
sealing
rotor
dual
oil
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
US00321235A
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English (en)
Inventor
D Eierman
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
Audi AG
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Filing date
Publication date
Application filed by Wankel GmbH, Audi AG filed Critical Wankel GmbH
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Publication of US3816041A publication Critical patent/US3816041A/en
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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
    • F01C19/08—Axially-movable sealings for working fluids
    • 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

Definitions

  • the oil seals function to prevent lubricating oil, which is delivered to the shaft eccentric area for lubricating the shaft bearings and/or passed to the interior of the rotor for effecting cooling of the latter, from flowing radially outwardly and into the working chambers of the rotary mechanism and contaminating the fluid therein and resulting in excessive oil consumption.
  • This oil seal construction prevents distortion of the oil seal under the pressure exerted by the oil entrapped in the space between the sealing legs in the area diametrically opposite the cresent-shaped vent opening, and the resultant lifting or disengagement of the oil seal, since the oil entering each of the plurality of chambers or spaces defined by the sealing edges and the ribs is entrapped and is thereby angularly accelerated to the speed of the rotor so as to be carried to where the resultant acceleration force causes the oil to flow out of each of the chambers as they come into registry with the crescent shaped vent opening.
  • gas vent passages are provided in the outer sealing edge.
  • Each gas vent passage shaped vent opening (the crescent-shaped vent opening being defined by a housing bore and the inner sealing surfaces of the oil seal) and exerts a pressure against the oil seal which lifts or unseats the seal from engagement with the housing end wall and allows passage of oil radially outwardly into the working chamresistant to disengagement due to the pressure of oil build up in the space between the sealing edges of the oil seal opposite the crescent-shaped vent opening.
  • a further object of this invention is to provide an improved oil seal of the dual-sealing type in which entrapment of gas which may leak past the outer sealing edge into the space between the sealing edges is obviated.
  • a still further object of this invention is to provide an improved dual-sealing oil seal which is capable of maintaining a continuous uniform abutment of the sealing surfaces againstthe adjacent housing end wall by preventing lifting or disengagement of the oil seal due to fluid pressure.
  • each of the chambers formed between the sealing edges and positioned to extend from the front end of the chamber outwardly therefrom at an angle to an imaginary radial line in the direction of rotor rotation.
  • This location of the vent passages minimizes the possibility of oil discharging through the vent passages because the oil, by reason of the acceleration and inertial forces, collects, relative to the direction of rotor rotation, in the trailing or rear 45' portion of the chambers.
  • the gas vent passages are also spaced from the adjacent rib to provide a sufficiently large collecting space for oil, which space preventsthe discharge of oil in the chambers from by-passing the outer sealing edge through the gas vent passages when the gas vent passages lie coextensive with the direction of the centrifugal force acting on oil in the chambers or, when the mechanism is nonoperating and the gas vent passages extend downwardly.
  • the seal has a channel or U-shape in cross-section with the legs, having at the ends thereof the sealing surfaces, inclined at approximately 60 from the plane of the housing end wall surface. It has also been found desirable that the legs be parallel and the width of the legs to be substantially the same and uniform through their effective lengths so that the sealing area, as wear of the legs occur, remains constant.
  • a supplemental oil seal ring may be provided in the rotor end face radially outwardly of the oil seal ring to further minimize the possibility of oil leaking into the space between the rotor and housing.
  • FIG. 1 is a fragmentary view in cross-section through the rotor and housing of a rotary mechanism of the Wankel type showing a dual-sealing edge oil seal according to this invention
  • FIG. 2 is a fragmentary view in elevation of the dualsealingedge oil seal shown in FIG. 1;
  • FIGS. 3 and 4- are schematic drawings of a rotary mechanism of the Wankel type showing the relationship of the dual-sealing edge oil seal to the housing bore which is located coaxially of the eccentric shaft and which bore defines with the oil seal a crescent-shaped vent opening; and w FIG. 5 is a fragmentary, cross-sectional viewof alternative construction of the oil seal according to this invention.
  • the reference number generally designates a dual-sealing edge oil seal, according to this invention, which is shown in association with a rotor 12 of a rotary mechanism 13 of the type disclosed in the U.S. Patent to Wankel et al, US. Pat. No. 2,988,065.
  • the oil seal 10 is mounted in a recess 14 formed in an end face 16 of rotor 12 and is resiliently biased to abut the surface 18 of the housing end wall 20 by'a suitable spring means, such as a Belleville spring 22 or an O-ring (not shown), or the like.
  • supplemental oil seal ring 24 which is biased by a suitable spring means, such as a Belleville spring 26 or the like, to abut housing end wall surface 18 and thereby assist in the prevention of the passage of oil through the interstice between housing end wall surface 18 and end face 16 of rotor 12.
  • gas seals 28 are also carried in the rotor end face 16 to abut the housing end wall surface 18 and thereby function to minimize the possibility of gas passing from the working chambers 32 through the space between rotor end face 16 and end wall surface I As best shown in FIGS.
  • rotor 12 is eccentrically mounted for rotation in the cavity formed by the housing (end wall 20 being a part of the housing) and defines with the housing a plurality of working chambers 32 which successively expand and contract in volumetric sizeas the rotor rotates.
  • the oil seal 10 slides along housing end wall 20 and is subject to varying amounts of centrifugal force during the course of a single revolution.
  • each of the oil seals 10 has a channel or general U-shape in cross-section withthe distal end sealing surfaces 40 of concentrically spaced annular legs 42 and 44 abutting the adjacent end wall surface 18,-The inner legs 42 and outer leg 44, extending from a body or base portion 38, define with end wall surface 18 an annular space which is divided into a plurality of arcuate chambers 46 by circumferentially spaced, radially extending ribs or webs 48 (see FIG. 2). As best illustrated in FIGS.
  • annular legs 42 and 44 and bore 36 are so dimensioned in diameter, that as the oil seal is carried in an orbital movement relative to bore 36, a portion of the periphery of bore 36 extends or overlaps a portion of inner leg 42, but never intersects the path of travel of outer leg 44.
  • the intersection or overlapping of bore 36 and inner leg 42 defines a crescent-shaped vent opening 50 which is represented by the hatching in FIGS. 3 and 4.
  • the vent opening 50 functions to communicate chambers 46 with the collecting groove (not shown), via bore 36.
  • the crescentshaped vent opening 50 is always diametrically opposite to the axis 30 of rotor 12 with respect to axis 52 of the shaft (not shown) and that oil in chambers 46 will be pumped out, through the vent opening 50, and into bore 36 due to the inertial forces on the oil being directed radially inwardly- (the inertial force being a resultant force of the summation of the acceleration forces directed radially inwardly and outwardly of the vent opening 50).
  • legs 42 and 44 slant radially inwardly from base or leg portion 38 toward the axis of the oil seal and housing end wall 20 at an angle of approximately from end wall surface 18. It is also advantageous to arrange legs 42 and 44 in parallel with each other and of uniform width so that sealing surfaces 40 in their sliding movement against wall surface 18 do not vary in width. It has been found desirable to provide legs 42 and 44 with a width of less than 1 mm, preferably 0.7 mm. To insure uniform, flat or planarabutment of sealing surfaces 40 of legs 42 and 44 as the oil seal wears, the legs 42 and 44 are constructed of a uniform width or with outer leg 44 slightly narrower in width than inner leg 42.
  • each of the chambers 46 is provided with a vent passageway means.
  • the vent passageway means may comprise grooves or channels 56 formed in sealing surface 40 of outer leg 44 of the oil seal.
  • Each of the channels 56 is located, relative to the direction of rotation of rotor 12 as shown by the arrow A in FIG. 2, in the leading or forward end portion of its associatedchamber 46 and extending from the chamber outwardly therefrom at an angle to an imaginary radial line in the direction of rotor rotation. Any accumulation of oil in each.
  • each channel 56 is spaced fromthe rib 48 forming the forward wall of the associated chamber 48 to thereby provide a catch basin or sump 58 for holding oil out of communication with the associated channel. It has been found that for most operating conditions spacing the channels from the rib a distance substantially equal to the distance between legs 42 and 44 provides a sump 58 for each chamber 48 of sufficient size toreceive the oil which may normally be expected in each of the chambers 48.
  • oil seal 10 has decreased consumption of oil to an extraordinary degree.
  • oil seal 10 In comparison tests of oil seal 10 with various conventional oil seals under the conditions of part-load operation at 5,000 rpm with a mean effective pressure of 1.6 kg/cm it was found, even after repeated tests, that oil consumption with oil seals 10 was many times less than with the conventional test oil seals.
  • FIG. 5 is shown an alternative construction of oil seal 10 which comprises two rings 60 and 62 joined together at 64 in any suitable manner, such as by welding the oil seal.
  • an improved duaLsealing oil seal having two substantially concentrically spaced sealing surfaces extending from a body portion and forming an annulus therebetween, the dual-sealing oil seal being carried by and disposed in a recess in the rotor end face with said sealing surfaces in sliding engagement against the adjacent side wall of the housing, the improvement comprising:
  • radial wall means in the annulus of said dualsealing oil seal for dividing said annulus into a plurality of recesses to cause oil in the recesses to be rotated with the oil seal and rotor and b. gas vent passage means for each of said recesses v disposed in the dual sealing oil seal to communicate the associated recess with the portion of the cavity surrounding the dual-sealing oil seal so as to pass gas from the associated recess into said cavity.
  • each of said gas vent passage means communicates with the leading end portion with respect to the direction of rotor rotation of the associated recess ata point spaced from the web forming the leading end of the recess to thereby provide an oil collecting sump when the rotor isstationary.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US00321235A 1972-01-21 1973-01-05 Oil seal for rotary mechanism Expired - Lifetime US3816041A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2202899A DE2202899C3 (de) 1972-01-21 1972-01-21 Innendichtung für einen Kolben einer Kreiskolbenmaschine

Publications (1)

Publication Number Publication Date
US3816041A true US3816041A (en) 1974-06-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00321235A Expired - Lifetime US3816041A (en) 1972-01-21 1973-01-05 Oil seal for rotary mechanism

Country Status (4)

Country Link
US (1) US3816041A (de)
JP (1) JPS4882208A (de)
CA (1) CA966869A (de)
DE (1) DE2202899C3 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2331677A1 (fr) * 1975-11-13 1977-06-10 Wankel Gmbh Joint interieur pour machines a piston rotatif

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3520720A1 (de) * 1985-06-10 1986-12-11 Wankel Gmbh, 1000 Berlin Innendichtung einer rotationskolbenmaschine
DE3609018A1 (de) * 1986-03-18 1987-09-24 Wankel Gmbh Axiale oeldichtung einer rotationskolbenmaschine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3168237A (en) * 1961-09-09 1965-02-02 Nsu Motorenwerke Ag Rotor cooling arrangement for rotary mechanisms
US3171590A (en) * 1960-12-16 1965-03-02 Curtiss Wright Corp Oil seal construction for rotary combustion engines
US3265045A (en) * 1962-12-21 1966-08-09 Daimler Benz Ag Rotary-piston internal combustion engine of trochoidal construction
US3400939A (en) * 1966-01-03 1968-09-10 Curtiss Wright Corp Oil seal construction for rotary engines
GB1180504A (en) * 1967-06-07 1970-02-04 Ustav Pro Vyzkum Motorovych Vo Rotary Piston Engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3171590A (en) * 1960-12-16 1965-03-02 Curtiss Wright Corp Oil seal construction for rotary combustion engines
US3168237A (en) * 1961-09-09 1965-02-02 Nsu Motorenwerke Ag Rotor cooling arrangement for rotary mechanisms
US3265045A (en) * 1962-12-21 1966-08-09 Daimler Benz Ag Rotary-piston internal combustion engine of trochoidal construction
US3400939A (en) * 1966-01-03 1968-09-10 Curtiss Wright Corp Oil seal construction for rotary engines
GB1180504A (en) * 1967-06-07 1970-02-04 Ustav Pro Vyzkum Motorovych Vo Rotary Piston Engine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2331677A1 (fr) * 1975-11-13 1977-06-10 Wankel Gmbh Joint interieur pour machines a piston rotatif
US4080120A (en) * 1975-11-13 1978-03-21 Wankel Gmbh Inner seal for rotary piston engines and method of making same

Also Published As

Publication number Publication date
DE2202899A1 (de) 1973-07-26
DE2202899C3 (de) 1980-05-22
JPS4882208A (de) 1973-11-02
CA966869A (en) 1975-04-29
DE2202899B2 (de) 1979-09-20

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