US3691999A - Liquid cooled housing for rotary piston engines - Google Patents

Liquid cooled housing for rotary piston engines Download PDF

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Publication number
US3691999A
US3691999A US41197A US3691999DA US3691999A US 3691999 A US3691999 A US 3691999A US 41197 A US41197 A US 41197A US 3691999D A US3691999D A US 3691999DA US 3691999 A US3691999 A US 3691999A
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US
United States
Prior art keywords
shell
ports
liquid
end parts
chambers
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
US41197A
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English (en)
Inventor
Rolf Lechler
Johannes Steinwart
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
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
Priority claimed from DE19691927859 external-priority patent/DE1927859C3/de
Application filed by Wankel GmbH, Audi AG filed Critical Wankel GmbH
Application granted granted Critical
Publication of US3691999A publication Critical patent/US3691999A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02B55/08—Outer members for co-operation with rotary pistons; Casings
    • F02B55/10—Cooling thereof
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Definitions

  • the invention relates to a liquid cooled housing for rotary piston engines, in particular internal combustion, consisting of at least one annular shell and two end parts, the housing having an inlet and an outlet connection for the cooling liquid, and the shell and end parts containing chambers in communication with each other and traversed by cooling liquid.
  • each end face of the shell is provided with a toroidal gasket on the outer circumference and a toroidal gasket on the inner circumference of the shell,
  • the problem therefore, is to avoid the disadvantages outlined above and provide a housing in which outward and inward leakage of cooling liquid is prevented by simple and inexpensive means.
  • This problem is solved, according to the invention, in that the ports for the cooling liquid in the joining end faces of the shell and end parts are individually sealed by packing rings encircling each of these openings.
  • the housing is intended for multiple rotary piston engines, and accordingly has several shells, with a housing head arranged in each instance between neighboring shells, chambers are provided, according to the invention, in the interhead that connect the cambers of the adjacent shells with each other, the ports for cooling liquid in the joining faces of the shells and interparts being again sealed individually by packing rings encircling said ports.
  • the head load notoriously varies greatly over the circumference of the housing. While the sector in which the intake and compression phases occur remains comparatively cool, the sector in which ignition, expansion in series, by means of the chambers in the end parts, in i such manner as to traverse first the spark plug sector, then the next sector towards the outlet passage, and then the sector around the outlet passage. At the same time, the cross sections of the several flow paths may be so proportioned as to provide the highest flow velocity I and hence the most rapid heat removal in the sector of greatest heat load.
  • the resistance to the flow of cooling liquid may be comparatively great, it is expedient in the interpart or interparts, inaddition to the chambers connecting the chambers of the adjacent shells with each other, to provide a chamber to carry off some of the cooling liquid flowing in out of the sector around the outlet passage of one of the adjacent shells.
  • the cooling liquid in this case is thus carried off parallel in the interparts and one end part.
  • the housing according to the invention When the housing according to the invention is used for a rotary piston internal combustion engine for vehicle propulsion, it is expedient to branch off, from the chamber of that end part which effects the first reversal of the liquid, a supply connection for the heat exchanger of the vehicle heating system, its drain connection communicating with the cooling liquid circuit return. Cooling liquid is thus bled for heating purposes at a point where there is a maximal pressure drop to the return, so that the heat exchanger is traversed at relatively high velocity. At this point, furthermore, hot water will be available quite soon after the engine is started, so the the heating system will respond quickly. Since the rotary piston internal combustion engine, by virtue of its shape, is advantageously installed in the vehicle with its lengthwise centerline parallel to the centerline of the vehicle.
  • the cooling liquid enters the front end part from the radiator in front, the connection for the heat exchanger is located at the rear end part, which results in short lines from said end part to the heat exchanger.
  • an oil cooler for the cooling liquid traversing the piston it is arranged at the front end part so that it will lie in the airstream and can be connected to the chamber in the front end part, which effects the second reversal of the cooling liquid in the housing.
  • FIG. I shows a developed section of the housing to exhibit the coolant circuit
  • FIG. 2 shows a view of the housing taken in the direction of arrow A in FIG. 1;
  • FIG. 3 shows a section at the line 3-3 in FIG. 1;
  • FIG. 4 shows a section at the line 4-4 in FIG. 1;
  • FIG. 5 shows a view of the right-hand end part of FIG. 1 in the direction of arrow D;
  • FIG. 6 shows a section at the line 6-6 in FIG. 3.
  • the liquid cooled housing shown consists of two end parts 1 and 2, an interpart 3 and two annular shells 4a and 4b each arranged between end part 1 or 2 and the interpart 3.
  • the inside surface 5 of each shell has the shape of a bilobate epitrochoid.
  • a piston not shown, is arranged eccentrically rotatable, which together with the inside surface 5 bounds three working spaces of varying volume, in each of which. a complete four-stroke cycle is effected.
  • an intake passage 6 to supply a fuel-air mixture
  • two spark plugs 7 and an exhaust passage 8 to carry off the burned gases are provided.
  • the housing In service, the housing is subjected to heating that varies greatly over the circumference, since in the sector from intake passage 6 to spark plugs 7 the intake and compression phase always occurs, and in the sector from spark plugs 7 to exhaust passage 8 the expansion and exhaust stroke alwaysoccurs.
  • Effective cooling near the spark plugs 7 is especially important, since empirically this is where the heat load is greatest.
  • Effective cooling of the shells is likewise especially critical, while the cooling of the end parts and interpart presents no particular problem.
  • Each shell 4a, 4b in the example of this embodiment, has three chambers 9, 10, and 11, traversed successively by cooling liquid as will be described later.
  • Chamber 9 is arranged in the sector of the spark plugs 7, chamber 10 in the following sector towards the exhaust passage 8, and chamber 11 in the sector of the exhaust passage 8. From each of these chambers, ports open into the two end walls of each shell, namely ports 12 and 13 for chamber 9, ports 14 and 15 for chamber 10 and ports 16 and 17 for chamber 11.
  • each shell 4 is provided with a through passage 18 to return the coolant after traversing the shells.
  • End part 1 has a hole 19 to accommodate a water pump 20 with flow volume regulator, connected by a line 21 to a liquid cooler, not shown.
  • the liquid delivered by pump 20 enters a chamber 22 in end part 1 and thence through ports 23, matching ports 12 and then passes into chamber 9 of the first shell 4a.
  • a chamber 24 is provided, whose ports 24a connect the ports 13 of the first shell 4a with ports 12 of the second shell 4b.
  • the cooling liquid passes through the ports 13 of this shell and ports 25 matching them in the adjoining end wall of end part 2 into a chamber 26 in this end part where the cooling liquid is reversed and can pass through ports 27 in the wall of end part 2 and ports 15 in the second shell 4b into the chamber 10 of this shell.
  • the ports 14 in the other end of shell 4b communicate through a chamber 28 and ports 28a in interpart 3 with the ports 15 in the first shell 4a, so that the cooling liquid can traverse chamber 10 of the first shell 4a and pass through ports 14 and matching ports 29 in the adjoining wall of end part 1 into a chamber 30 in end part 1.
  • the cooling liquid is reversed again, passing through ports 31 and matching ports 16 in the first shell 4a into the chamber 1 1 of this shell.
  • the liquid leaves chamber 11 through ports 17 and their matching ports 32 into a chamber 33 of interpart 3, communicating through ports 34 with the ports 16 in the second shell 4b and through ports 35 with the passages 18 in shell 4a and 4b.
  • the liquid passes through ports 17 and their matching ports 36 in the adjoining wall of end part 2 into a chamber 37 in this end part, communicating through a port 38 with the passage 18 of the adjoining shell 4b.
  • the passage 18 of the first shell 40 opens into a return chamber 39 in the first end part 1, communicating by a line 40 with the other end of the liquid cooler, not shown, and through a by-pass 41 controlled by the flow control valve in pump-20 with the chamber 22 in end part 1.
  • the cooling liquid thus flows into the chamber 22 of end part 1, successively traverses the chambers 9 of shells 4a and 4b, is reversed by chamber 26 in end part 2, traverses the chambers 10 of the shells, is again reversed by chamber 30 inthe first end part 1, traverses the chamber 11 of the first shell 4a, is divided at that point into two parallel flows one of which is routed through chamber 33 in interpart 3 and port 35 into the passage 18 of shell 4a and the other through the chamber 11 of the second shell 4b, thence to flow into chamber 37 of end part 2 and drain off through port 38 and the passages 18.
  • the internal combustion engine serves to propel a motor vehicle, it is expedient to arrange the lengthwise centerline of the housing parallel to the vehicle centerline, with the left-hand end of the housing in FIG. 1 in the direction of travel.
  • the pistons of the rotary piston internal combustion engine are oil cooled, the oil cooler is arranged in the airstream and connected to passages 44, 45' leading from chamber 30 in the first end part 1 and thus traversed by the cooling liquid.
  • two passages 46, 47 may be provided in the second end part 2, of which passage 46 leads from chamber 26 and supplies hot water to the heat exchanger of the heating system and passage 47 carries the water, after traversing the heat exchanger, into the chamber 37 of end part 1 communicating with the return. This affords the maximum pressure differential between the inlet and outlet sides of the heat exchanger, so that it is traversed at high flow velocity and the heating system responds very quickly.
  • the cooling liquid flow is divided into two parts, so that the cooling liquid is returned in parallel streams. This keeps theflow resistance of the entire return circuit from taking too high a value. This is especially important in engines where more than two units are placed in tandem.
  • the invention is not limited to the embodiment shown by way of example, in particular not to a twounit engine. Rather the invention may be applied with the like advantages to an engine having only one shell or to an engine havingmore than two shells and a corresponding larger number of interparts.
  • a rotary piston engine having liquid cooled housing consisting of at least one annular shell and two end parts, the housing having an inlet and an outlet connection for a coolant liquid and the shell and end parts containing chambers in communication with each other, a coolant liquid, where the coolant liquid flows axially through the passages of the shell, means for reversing the flow .of the liquid in the chambers of the end parts, and the coolant liquid ports in the joining faces of the shell and end parts being sealed individualiy by means of packing rings encircling such ports.
  • a multiple rotary piston engine having a plurality of shells, a housing interpart being arranged in each instance between neighboring shells, chambers are provided in the interpan connecting the chambers of the neighboring shells with each other, the coolant liquid ports in the joining faces of the shells and interpart being individually sealed by means of packing rings encircling said ports.
  • a liquid cooled housing according to claim 2 wherein a chamber is provided in the interpart to divert some of the cooling liquid coming in out of the chamber embracing the exhaust passage of one of the adjoining shells.
  • a liquid cooled housing for rotary piston engines consisting of at least one annular shell and two end parts, the housing having an inlet and an outlet connection for a coolant liquid and the shell and end parts containing chambers in communication with each other, a coolant liquid, where the coolant liquid flows axially through the passages of the shell, and means for reversing the flow of the coolant liquid in the chambers of the end parts, the coolant liquid ports in the joining faces of the shell and end parts being sealed individually by means of packing rings encircling such ports, a spark plug sector and an exhaust passage, the chambers of the shell being connected in series by the chambers of the end parts in such manner that first the spark plug sector, then the sector following towards the exhaust passage, and then the sector around the exhaust passage are traversed by cooling liquid.
  • the engine is for vehicle propulsion and includes a heat exchanger of a vehicle heating system wherein a supply connection for the heat exchanger of a'vehicle heating system branches off from the chamber of that end part which effects the first reversal of the liquid, the outlet connection of the heat exchanger communicating with the return of the coolant liquid circuit.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
US41197A 1969-05-31 1970-05-28 Liquid cooled housing for rotary piston engines Expired - Lifetime US3691999A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19691927859 DE1927859C3 (de) 1969-05-31 FlUssigkeitsgekühltes Gehäuse für eine Rotationskolbenmaschine, insbesondere Rotationskolben-Brennkraftmaschine

Publications (1)

Publication Number Publication Date
US3691999A true US3691999A (en) 1972-09-19

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ID=5735764

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US41197A Expired - Lifetime US3691999A (en) 1969-05-31 1970-05-28 Liquid cooled housing for rotary piston engines

Country Status (4)

Country Link
US (1) US3691999A (enrdf_load_stackoverflow)
JP (1) JPS5039208B1 (enrdf_load_stackoverflow)
FR (1) FR2050401B1 (enrdf_load_stackoverflow)
GB (1) GB1310128A (enrdf_load_stackoverflow)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3743452A (en) * 1971-05-10 1973-07-03 Audi Ag Liquid cooling system for rotary piston engines
US3799708A (en) * 1971-07-31 1974-03-26 Volkswagenwerk Ag Cooling arrangement for a combustion engine having a rotary type piston
US3907468A (en) * 1974-05-22 1975-09-23 Gen Motors Corp Rotary engine cooling system
US3942919A (en) * 1972-11-08 1976-03-09 Toyo Kogyo Co., Ltd. Rotary piston type engine
US3969048A (en) * 1973-05-18 1976-07-13 Daimler-Benz Aktiengesellschaft Rotary piston internal combustion engine of trochoidal construction
US4915603A (en) * 1988-08-01 1990-04-10 Brunswick Corporation Rotary engine cooling system
US20040200217A1 (en) * 2003-04-08 2004-10-14 Marchetti George A Bladed heat transfer stator elements for a stirling rotary engine
RU2291312C1 (ru) * 2005-07-12 2007-01-10 Государственное образовательное учреждение высшего профессионального образования "Таганрогский государственный радиотехнический университет" (ТРТУ) Роторный двигатель
US20180202357A1 (en) * 2017-01-16 2018-07-19 Pratt & Whitney Canada Corp. Turbofan engine assembly with intercooler
US10450952B2 (en) 2017-01-16 2019-10-22 Pratt & Whitney Canada Corp. Turbofan engine assembly with gearbox
EP3650734A1 (en) * 2018-02-02 2020-05-13 LS Mtron Ltd. Cooling apparatus for hydrostatic transmission
US20250084783A1 (en) * 2023-09-11 2025-03-13 Pratt & Whitney Canada Corp. Rotary engine and cooling systems thereof

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2353965A (en) * 1941-06-18 1944-07-18 Meador Calender Corp Rotary pump or compressor
GB974370A (en) * 1961-05-09 1964-11-04 Schweizerische Lokomotiv Rotary compressor with cooled housing and housing cover
US3289647A (en) * 1964-08-24 1966-12-06 Curtiss Wright Corp Cooling system for multi-unit rotary mechanisms

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS434001Y1 (enrdf_load_stackoverflow) * 1965-08-31 1968-02-21

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2353965A (en) * 1941-06-18 1944-07-18 Meador Calender Corp Rotary pump or compressor
GB974370A (en) * 1961-05-09 1964-11-04 Schweizerische Lokomotiv Rotary compressor with cooled housing and housing cover
US3289647A (en) * 1964-08-24 1966-12-06 Curtiss Wright Corp Cooling system for multi-unit rotary mechanisms

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3743452A (en) * 1971-05-10 1973-07-03 Audi Ag Liquid cooling system for rotary piston engines
US3799708A (en) * 1971-07-31 1974-03-26 Volkswagenwerk Ag Cooling arrangement for a combustion engine having a rotary type piston
US3942919A (en) * 1972-11-08 1976-03-09 Toyo Kogyo Co., Ltd. Rotary piston type engine
US3969048A (en) * 1973-05-18 1976-07-13 Daimler-Benz Aktiengesellschaft Rotary piston internal combustion engine of trochoidal construction
US3907468A (en) * 1974-05-22 1975-09-23 Gen Motors Corp Rotary engine cooling system
US4915603A (en) * 1988-08-01 1990-04-10 Brunswick Corporation Rotary engine cooling system
US20040200217A1 (en) * 2003-04-08 2004-10-14 Marchetti George A Bladed heat transfer stator elements for a stirling rotary engine
RU2291312C1 (ru) * 2005-07-12 2007-01-10 Государственное образовательное учреждение высшего профессионального образования "Таганрогский государственный радиотехнический университет" (ТРТУ) Роторный двигатель
US20180202357A1 (en) * 2017-01-16 2018-07-19 Pratt & Whitney Canada Corp. Turbofan engine assembly with intercooler
US10450952B2 (en) 2017-01-16 2019-10-22 Pratt & Whitney Canada Corp. Turbofan engine assembly with gearbox
US10634049B2 (en) * 2017-01-16 2020-04-28 Pratt & Whitney Canada Corp. Turbofan engine assembly with intercooler
US11401890B2 (en) 2017-01-16 2022-08-02 Pratt & Whitney Canada Corp. Turbofan engine assembly with intercooler
EP3650734A1 (en) * 2018-02-02 2020-05-13 LS Mtron Ltd. Cooling apparatus for hydrostatic transmission
US20250084783A1 (en) * 2023-09-11 2025-03-13 Pratt & Whitney Canada Corp. Rotary engine and cooling systems thereof
US12264616B1 (en) * 2023-09-11 2025-04-01 Pratt & Whitney Canada Corp. Rotary engine and cooling systems thereof

Also Published As

Publication number Publication date
FR2050401A1 (enrdf_load_stackoverflow) 1971-04-02
FR2050401B1 (enrdf_load_stackoverflow) 1973-04-06
DE1927859B2 (de) 1977-02-03
GB1310128A (en) 1973-03-14
JPS5039208B1 (enrdf_load_stackoverflow) 1975-12-15
DE1927859A1 (de) 1970-12-10

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