US3206109A - Fluid cooling means for rotors of rotary mechanisms - Google Patents

Fluid cooling means for rotors of rotary mechanisms Download PDF

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Publication number
US3206109A
US3206109A US344396A US34439664A US3206109A US 3206109 A US3206109 A US 3206109A US 344396 A US344396 A US 344396A US 34439664 A US34439664 A US 34439664A US 3206109 A US3206109 A US 3206109A
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United States
Prior art keywords
rotor
compartments
compartment
radially
cooling
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Expired - Lifetime
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US344396A
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English (en)
Inventor
Paschke Hanns-Dieter
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
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Wankel GmbH
NSU Motorenwerke AG
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    • 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
    • F02B55/00—Internal-combustion aspects of rotary pistons; Outer members for co-operation with rotary pistons
    • F02B55/02—Pistons
    • F02B55/04—Cooling thereof

Definitions

  • the present invention is directed to improvement in the fluid cooling means described in US. Patent 3,102,682, issued on September 3, 1963 and assigned to the same assignee as the present invention.
  • the rotor of the rotary mechanism is mounted so as to rotate on a rotating eccentric and makes a planetary circulating movement relative to the external housing or outer body.
  • the rotor is acted upon by acceleration forces which periodically reverse in direction and therefore any cooling liquid within the rotor and movable therewith is subject to the same periodic reversal of the acceleration forces.
  • the rotor of the present invention is provided with a plurality of separate circumferentially-spaced internal compartments with openings for supplying and draining the cooling fluid from said compartments.
  • the cooling liquid When the acceleration forces on a particular rotor compartment are directed radially outwardly the cooling liquid is thrown into said compartments through an inlet opening and upon reversal of the acceleration forces the cooling liquid is thrown radially inwardly and out of the outlet opening of said compartment. As the coolant flows out of the outlet opening it can be collected for recirculation through the interior of the rotor after suitable removal of the heat from the cooling fluid.
  • the present invention has for its prime object providing means for reducing the amount of cooling medium circulated through the interior of the rotor while maintaining maximum cooling effectiveness of the rotor interior walls.
  • the invention is generally carried out by providing a plurality of circumferentially spaced cooling compartments in the interior of the rotor and providing openings thereto for supplying and draining the cooling fluid with said openings being so located with respect to the direction of the circulating fluid, when the acceleration forces acting on a particular rotor compartment are directed radially inwardly, the cooling fluid within the rotor compartment will not be completely drained from 3,206,109 Patent-ed Sept. 14, 1965 said compartment but some of said cooling fluid will be mixed with incoming cooling fluid so as to increase the volume of cooling fluid available for cooling the rotor Walls.
  • the total volume of oil within each rotor compartment will be maintained without requiring a total increase in the volume of oil required for circulation through the entire rotor interior.
  • FIG. 1 is an axial sectional view of a rotary mechanism embodying the invention
  • FIG. 2 is a sectional view taken along line 2-2 of FIG. 1 and diagrammatically illustrating the cooling fluid in the cooling compartments,
  • FIGS. 3-8 are views similar to FIG. 2 and diagrammatically illustrating the oil circulation in portions of the interior rotor at different states of rotor rotation, and
  • FIG. 9 is an axial sectional view of the rotary mechanism illustrating another embodiment of the invention.
  • the rotary mechanism 10 is composed of an outer body including a pair of end walls 12 and 14 interconnected by a peripheral wall 16 to form a cavity therein.
  • the profile of the inner surface 18 of the outer body peripheral Wall 16 is preferably basically a two-lobed epitrochoid (FIG. 2).
  • a shaft 20 is mounted coaxially with the cavity formed by the outer body and is rotatable relative to said outer body.
  • the shaft 20 has an eccentric portion 22 formed thereon upon which is rotatably mounted a rotor 24 having a multilobed profile and whose outer peripheral wall 26 forms a plurality of circumferentially-spaced apex portions for sealing engagement with the inner surface 18 of the outer body peripheral wall 16.
  • the rotor has three apex portions and the multilobed cavity of the outer body has two-lobed portions although other combinations are possible.
  • Seal strips 28 are provided in each of the apex portions of the rotor 24 and extend from one end face of the rotor to the other end face and are in continuous sealing engagement with the inner surface 18 of the outer body peripheral wall 16 to form a plurality of working chambers 30 which during relative rotation vary in volume.
  • the apex seals 28 mate with intermediate seal bodies 32 also provided in each of the apex portions of the rotor and with side seals 34 provided in each of the end walls 36 and 38, re-
  • the rotor 26 is supported on the eccentric portion 22 by a sleeve-type bearing 40.
  • Suitable bearings 42 are also provided for supporting the rotating shaft 20 in the outer body housing and surrounding bearings 42 on one side of the mechanism is an externally toothed gear 44 which meshes with an internally toothed gear 46 either supported by the rotor end wall 36 or made integral with a portion of said end wall 36.
  • the gears 42 and 44 serve to help rotatably position the rotor with respect to the epitrochoidal surface of the peripheral wall 16 but do not drive or impart torque to the shaft 20.
  • the ratio of rotation of the shaft with respect to the rotor is 3:1 wherein for each rotation of the rotor about is axis the shaft rotates three times about its axis with the axes of the shaft and rotor being designated as M M in FIG. 2, respectively.
  • An intake port 48 is provided for admitting air and/or a fuel-air mixture, an ignition means 50 may be provided for igniting the mixture and an exhaust port 52 is provided for expelling the burnt gases so that the stages of intake, compression, expansion and exhaust may be carried out.
  • an inlet passageway 54 may be provided in the end wall 12 of the outer body and may be suitably connected to a pump and fluid reservoir (not shown) for pumping the fluid through a passageway 54 and into an annular cavity 56 between the rotor and the housing end wall 12.
  • the rotor 24 is made hollow and is provided with a plurality of axially-extending interior walls or partitions 60 with said partitions 69 being circumferentially-spaced around the rotor 24 to divide the rotor interior into a plurality of cirumferentially-spaced cooling compartments 58.
  • the partitions 69 extend in an avial direction from one end wall 36 of the rotor to the opposite end wall 38 and in a radial direction from the rotor peripheral wall 26 radially inward to the rotor hub or the radially interior wall 62 of the rotor.
  • an inlet passageway 64 is provided in the wall 36 of the rotor and has an inlet opening 66 to each of the compartments 58.
  • An oulet passageway 68 for each compartment is provided in the end wall 38 of the rotor and has an outlet opening '79 communicating with the interior of each compartment 58.
  • the relationship between the inlet opening 66 and the outlet openings 70 for each rotor compartment 58 with respect to the rotor end walls 36 and 38 is significant to the operation of the invention.
  • acceleration forces are generated which act substantially in the direction of maximum eccentricity of the eccentric portion 22.
  • any fluid present in the annular cavity 56 or in the rotor compartment will be thrown radially outwardly in response to the acceleration forces and the fluid on the opposite side of the mechanism or the downward side will be thrown radially inwardly with respect to the rotor compartments 58.
  • the acceleration forces will periodically change direction with respect to said rotor.
  • the fluid present in the cavity 56 will therefore be thrown radially outward into the inlet passageway 64 and out of the inlet passageway opening 66 to the compartments 58 and during a reversal of the direction of the acceleration forces the fluid in the compartments 58 will then be thrown radially inwardly and into the outlet opening 70 and out of the outlet passageway 68 and will drain into an annular collection scoop member 72 to which is connected an outlet passageway 74 in the outer body end wall 14 for draining the fluid out of the rotary mechanism and to a suitable cooling means.
  • the cooling fluid may then be recirculated through the rotor so that the same cooling fluid may be used over again.
  • Annular seals 76 are provided between each of the rotor end walls 36 and 38 and the housing end walls 12 and 14, respectively, to prevent leakage of the cooling fluid radially outwardly into the working chambers 30 of the rotary mechanism.
  • the present invention overcomes this disadvantage by providing a relationship between the inlet and outlet openings for each compartment wherein the cooling fluid is not completely drained from each compartment so that a lesser amount is required during the filling cycle portion which therefore results in a lesser total amount of cooling fluid being required to maintain maximum cooling of the rotor interior.
  • the inlet opening 66 and the outlet opening 70 are disposed so that they are spaced radially outwardly a substantial distance from the radially innermost portion of their respective rotor compartment 58.
  • theoutlet openings 70 are disposed so that they are spaced from the partitions 60 in a circumferential direction and spaced from the rotor peripheral wall 26 and the rotor inner wall 62 in a radial direction.
  • the openings 66 for supplying cooling fluid to the compartments 58 are similarly disposed with respect to the compartment walls of said compartments'SS. As described above, this arrangement results in a residual amount of cooling fluid remaining behind in each chamher during the drainage portion of the cycle.
  • two compartments 58a and 58b are shown at a stage of rotation wherein such compartments are substantially at the position of maximum eccentricity of the shaft rotation and the cooling fluid therein is shown during the supply phase.
  • the cooling fluid at this time is thrown into said compartments and collects adjacent the inner surface the rotor peripheral Wall 26.
  • the cooling fluid will be seen as rotating around the inner surfaces of the walls of the compartment 58 in the direction of rotor rotation until when the rotor has reached the position shown in FIG.
  • FIG. 9 shows a second embodiment of the invention which is substantially identical to the embodiment illustrated in FIG. 1 and bears similar numeral designations.
  • the compartments 58' have no outlet passageway 68 and outlet openings 70' so that during the drainage phase of the cycle, any drainage from these compartments will have to flow back through the inlet opening 66'. Therefore, a greater amount of residual cooling fluid will remain in these compartments and that which drains out of these compartments will mix with the incoming supply of cooling fluid from the cooling supply cavity 56'.
  • some of the compartments must be provided with outflow openings 70 as in the embodiment of FIG. 1, to provide for a complete exchange of the cooling fluid during operation of the mechanism.
  • a novel and improved cooling mechanism is provided for the interior of the rotor in a rotary mechanism.
  • a substantially smaller amount of cooling fluid is required to cool the rotor in terior while still maintaining maximum cooling effectiveness.
  • the invention also has the advantage that a smaller supply reservoir, cooling recirculating mechanism and oil pump may be used which reduces the weight of the entire cooling unit.
  • a rotary mechanism having an outer body comprising a peripheral wall interconnected with a pair of parallel end walls defining a cavity; a rotatable shaft mounted in said outer body coaxial with the axis of said outer body peripheral wall and having an eccentric portion; a rotor rotatably supported on said eccentric portion for rotation about its axis while describing a planetary motion relative to the axis of said outer body peripheral wall whereby acceleration forces are generated in said rotor which successively change direction relative to said rotor, said rotor having a hub portion and a peripheral wall interconnected with a pair of parallel end walls defining a cavity therein with said cavity having a plurality of circumferentially-spaced, axially-extending partitions dividing said cavity into a plurality of compartments over the entire circumference thereof; an inlet opening for each of said compartments in one of said rotor end walls for supplying a cooling liquid to each said compartment when the acceleration forces are directed substantially radially outwardly relative to each said compartment, said inlet opening being
  • each of said rotor compartments is provided with an inlet and an outlet opening.
  • a rotary mechanism having an outer body comprising a peripheral wall interconnected with a pair of parallel end walls defining a cavity; a rotatable shaft mounted in said outer body coaxial with the axis of said outer body peripheral wall and having an eccentric portion; a rotor rotatably supported on said eccentric portion for rotation about its axis while describing a planetary motion relative to the axis of said outer body peripheral wall whereby acceleration forces are generated in said rotor which successively change direction relative to said rotor, said rotor having a hub portion and a peripheral wall interconnected with a pair of parallel end Walls defining a cavity therein with said cavity having a plurality of circumferentially-spaced, axially-extending partitions dividing said cavity into a plurality of compartments over the entire circumference thereof; an inlet opening for each of said compartments in one of said rotor end walls for supplying a cooling liquid to each said compartment when the acceleration forces are directed substantially radially outwardly relative to each said compartment, and a single outlet

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US344396A 1963-03-07 1964-02-12 Fluid cooling means for rotors of rotary mechanisms Expired - Lifetime US3206109A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DEN22853A DE1224982B (de) 1963-03-07 1963-03-07 Fluessigkeitskuehlung fuer Kolben von Kreiskolbenmaschinen

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DE (1) DE1224982B (de)
GB (1) GB1027983A (de)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3299864A (en) * 1964-11-13 1967-01-24 Renault Rotary-engine rotors
US3299863A (en) * 1964-04-04 1967-01-24 Renault Rotors of rotary engines
US3302624A (en) * 1964-06-24 1967-02-07 Toyo Kogyo Company Ltd Rotary piston and cooling means therefor
US3303829A (en) * 1964-04-03 1967-02-14 Renault Rotors for rotary engines
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
US3400939A (en) * 1966-01-03 1968-09-10 Curtiss Wright Corp Oil seal construction for rotary engines
US3655302A (en) * 1970-04-02 1972-04-11 Curtiss Wright Corp Rotor and gear assembly for rotary mechanisms
US3836294A (en) * 1971-12-24 1974-09-17 Audi Ag Piston for rotary piston machines and means for its manufacture
US3887307A (en) * 1974-04-30 1975-06-03 Curtiss Wright Corp Rotary mechanism with die-cast trochoidal housing
US20110023814A1 (en) * 2008-08-04 2011-02-03 Liquidpiston, Inc. Isochoric Heat Addition Engines and Methods
US20120294747A1 (en) * 2011-03-29 2012-11-22 Liquidpiston, Inc. Cycloid Rotor Engine
US8794211B2 (en) 2004-01-12 2014-08-05 Liquidpiston, Inc. Hybrid cycle combustion engine and methods
US8863723B2 (en) 2006-08-02 2014-10-21 Liquidpiston, Inc. Hybrid cycle rotary engine
US9528435B2 (en) 2013-01-25 2016-12-27 Liquidpiston, Inc. Air-cooled rotary engine
US9593580B2 (en) * 2012-11-23 2017-03-14 Pratt & Whitney Canada Corp. Wankel engine rotor
US11994165B2 (en) 2022-03-01 2024-05-28 General Electric Company Lubricant supply system

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3102682A (en) * 1961-02-10 1963-09-03 Nsu Motorenwerke Ag Neckarsulm Liquid cooling for the rotor of a rotating-piston engine
US3112870A (en) * 1961-06-06 1963-12-03 Curtiss Wright Corp Air cooled rotor for rotary mechanism

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3102682A (en) * 1961-02-10 1963-09-03 Nsu Motorenwerke Ag Neckarsulm Liquid cooling for the rotor of a rotating-piston engine
US3112870A (en) * 1961-06-06 1963-12-03 Curtiss Wright Corp Air cooled rotor for rotary mechanism

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3303829A (en) * 1964-04-03 1967-02-14 Renault Rotors for rotary engines
US3299863A (en) * 1964-04-04 1967-01-24 Renault Rotors of rotary engines
US3302624A (en) * 1964-06-24 1967-02-07 Toyo Kogyo Company Ltd Rotary piston and cooling means therefor
US3299864A (en) * 1964-11-13 1967-01-24 Renault Rotary-engine rotors
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
US3400939A (en) * 1966-01-03 1968-09-10 Curtiss Wright Corp Oil seal construction for rotary engines
US3333763A (en) * 1966-02-02 1967-08-01 Nsu Motorenwerke Ag Sealing arrangement for rotary engines
US3655302A (en) * 1970-04-02 1972-04-11 Curtiss Wright Corp Rotor and gear assembly for rotary mechanisms
US3836294A (en) * 1971-12-24 1974-09-17 Audi Ag Piston for rotary piston machines and means for its manufacture
US3887307A (en) * 1974-04-30 1975-06-03 Curtiss Wright Corp Rotary mechanism with die-cast trochoidal housing
US8794211B2 (en) 2004-01-12 2014-08-05 Liquidpiston, Inc. Hybrid cycle combustion engine and methods
US9523310B2 (en) 2004-01-12 2016-12-20 Liquidpiston, Inc. Hybrid cycle combustion engine and methods
US8863723B2 (en) 2006-08-02 2014-10-21 Liquidpiston, Inc. Hybrid cycle rotary engine
US9644570B2 (en) 2006-08-02 2017-05-09 Liquidpiston, Inc. Hybrid cycle rotary engine
US20110023814A1 (en) * 2008-08-04 2011-02-03 Liquidpiston, Inc. Isochoric Heat Addition Engines and Methods
US8863724B2 (en) 2008-08-04 2014-10-21 Liquidpiston, Inc. Isochoric heat addition engines and methods
US9382851B2 (en) 2008-08-04 2016-07-05 Liquidpiston, Inc. Isochoric heat addition engines and methods
US20120294747A1 (en) * 2011-03-29 2012-11-22 Liquidpiston, Inc. Cycloid Rotor Engine
US8523546B2 (en) * 2011-03-29 2013-09-03 Liquidpiston, Inc. Cycloid rotor engine
US9593580B2 (en) * 2012-11-23 2017-03-14 Pratt & Whitney Canada Corp. Wankel engine rotor
US9528435B2 (en) 2013-01-25 2016-12-27 Liquidpiston, Inc. Air-cooled rotary engine
US11994165B2 (en) 2022-03-01 2024-05-28 General Electric Company Lubricant supply system

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DE1224982B (de) 1966-09-15
GB1027983A (en) 1966-05-04

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