US3743452A - Liquid cooling system for rotary piston engines - Google Patents

Liquid cooling system for rotary piston engines Download PDF

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Publication number
US3743452A
US3743452A US00245588A US3743452DA US3743452A US 3743452 A US3743452 A US 3743452A US 00245588 A US00245588 A US 00245588A US 3743452D A US3743452D A US 3743452DA US 3743452 A US3743452 A US 3743452A
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US
United States
Prior art keywords
cooling
passageway
inlet
liquid
passageways
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
US00245588A
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English (en)
Inventor
J 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 DE19712123010 external-priority patent/DE2123010C3/de
Application filed by Wankel GmbH, Audi AG filed Critical Wankel GmbH
Application granted granted Critical
Publication of US3743452A publication Critical patent/US3743452A/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

Definitions

  • a liquid cooling system for a rotary piston, internal combustion engine having cooling passageways, including an inlet cooling passageway, in the engine housing which are connected together at opposite ends to provide series flow of cooling liquid therethrough the system comprises a cooling liquid inlet port in the engine a housing communicating with a liquid cooler and the inlet cooling passageway.
  • An outlet port is provided in the engine housing to connect the cooling passages I with the liquid cooler to pass heated cooling liquid to the latter.
  • a liquid circulating pump is disposed at the end of the engine housing opposite from the inlet port and in communication with the inlet cooling passageway to draw cooling liquid through the inlet port and inlet cooling passageway and force cooling liquid through the other liquid cooling passageways and the outlet port.
  • a bypass passageway is provided to com-.
  • the invention relates to rotary piston engines and, more particularly, to a liquid cooling system for rotary piston, internal combustion engines.
  • Another object of this invention is to provide a liquid cooling system for a rotary piston, internal combustion engine in which system resistance to liquid flow to and into the ciruclatin'g pump is minimized so that the cirpumps in conventional systems of comparable size.
  • a further object of this invention is to provide for a rotary piston, internal combustion engine, a liquid cooling system in which full liquid cooling flow can be maintained in the cooling flow passages in the hottest region of the engine housing during the period when the liquid cooler of the system is being bypassed.
  • a still further object of the present invention is to provide for a rotary piston, internal combustionengine, a liquid cooling system in which more space is made available for accessory devices at the accessory drive end portion of the engine.
  • culating pump size can be smaller than circulating 55.
  • this invention contemplates for a rotary piston, internal combustion engine an improved liquid cooling system which comprises'a-plurality of cooling passageways, including a straight, relatively large inlet cooling passageway, which are connected together at opposite ends to provide series flow of cooling liquid through the cooling passageways.
  • An inlet port is provided in the engine housing at one end portion thereof, which port is in communication with a liquid cooler to receive cooled liquid from the latter and with the inlet cooling passageway to pass cooled liquid to such passageway.
  • An outlet port is provided in the engine housing to communicate with the liquid cooling passageways to receive heated cooling liquid from the latter and with the liquid cooler to pass the heated cooling liquid to the cooler for cooling before recirculation to the inlet port.
  • a liquid circulating pump is disposed at the end of the engine housing opposite from the inlet port and in communication with the inlet cooling passageway and the other cooling passageways to draw cooling liquid through the inlet cooling passageway and force the same into and through the other cooling passageways.
  • a bypass passageway is provided to communicate the other liquid cooling passageways with the inlet port and inlet cooling passageway.
  • a thermostatically controlled valve is disposed at the inlet port to regulate flow through the bypass passageway and, when fully open, permit flow of cooling liquid to the inlet port, via the bypass passageway, and thus bypass the liquid cooler.
  • the inlet cooling passageway and the cooling passageway receiving the discharge from the circulating pump are located in the area of the engine housing which is subjected to the highest heat flux so that during periods when the thermostatically controlled valve is fully open and the cooler is being bypassed there is circulation of cooling liquid past the hottest area of the engine housing.
  • FIG. 1 is a schematic drawing of the liquid cooling system according to this invention.
  • FIG. 2 is an exploded view of a rotary piston, internal combustion engine having a liquid cooling system shown in FIG. 1, the liquid cooler and conduits being omitted;
  • FIG. 3 is a transverse cross-sectional view, through the engine housing section in which a thermostatically controlled valve is located.
  • engine 12 is shown and will be described as a single rotor engine having a housing composed of a plurality of sections, but it is to be understood that the invention is not limited to such engine.
  • the liquid cooling system of this invention has application to rotary piston internal combustion engines having two or more rotary pistons and comprising any number of housing sections.
  • engine 12 comprises three main housing sections, an intermediate section 14 having an epitrochoidal shaped internal surface 16 and two end wall sections 18 and 20.
  • the end wall section 18 is provided with an inlet port 22 which communicates through an opening 24 with a passage or channels 26 and 28 in intermediate section 16 and end wall section 20.
  • the opening 26 and channels 26 and 28 are in register to form a relatively large, straight inlet passageway 30.
  • the channel 28 in end wall section 20, at the opposite end of passageway 30, serves as a pump inlet or suction port for a centrifugal pump which has an impeller 32 mounted for rotation in a scroll cavity 34 formed in end wall section 20.
  • the pump has a discharge port 36 which communicates with a header chamber 38 formed in end wall section 20.
  • the intermediate section 14 and the two end wall sections 18 and 20 are provided with a plurality of cooling liquid passageways 40, 42 and 44 which are similar to and extend substantially parallel to inlet passageway 30.
  • each passageway 40, 42 and 44 may comprise two or more streams formed by sets of aligned channels in housing sections 14, 16 and 20.
  • Each of the passageways 30, 40, 42 and 44 are interconnected with each other at their opposite ends with header chambers formed in end wall sections 18 and 20 to thereby provide for serial flow of cooling liquid through the passageways.
  • the passageway 40 is in communication at one end with header chamber 38 to receive cooling liquid discharged by impeller 32 of the circulating pump.
  • passageway 40 communicates with a transfer header chamber 48 in end wall section 18.
  • the passageway 42 communicates with transfer header chamber 48 and, at the opposite end, with a second transfer header chamber 50 formed in end wall section 20 (see FIG. 2).
  • the passageway 44 connects, at one end, with second transfer header chamber 50 in end wall section 20 to receive cooling liquid from the latter and, at the opposite end, communicates with a discharge header chamber 52 in endwall section 18 (see FIG. 3).
  • the end wall section 18 is also provided with an outlet passage and port 54 which communicates with discharge header chamber 52.
  • the cooling system further includes, as shown in FIG. 1, an inlet conduit 70 which interconnects inlet port 22 of engine 12 and cooler 56 and an outlet conduit 72 which is connected to cooler 56 and outlet passage and port 54 of engine 12.
  • the cooler 56 may be I the conventional radiator employed in automobiles.
  • the inlet conduit 70 provides for conducting cooled liquid coolant from cooler 56 to inlet port 22 of engine 12, while outlet conduit 72 provides for conducting heated liquid coolant from outlet passage and port 54 to the cooler 56 where it is cooled before recirculation to engine 12 via inlet conduit 70.
  • the cooling system 10 further includes a thermostatic valve 66 disposed in inlet 22 in end wall section 18 of the engine housing and a relatively straight and unrestricted inlet passageway interconnecting inlet 22 with a circulating pump at end wall section 20 located at the opposite end of the engine housing.
  • This arrangement provides minimal restriction in liquid flow to the circulating pump and eliminates cavitation in the circulating pump so that the circulating pump functions at optimum efficiency.
  • the thermostatic valve 66 at a point remote from the circulating pump more room is provided at the end wall section 20 (the accessory drive end).
  • the cooling system 10 provides for regulation of cooling liquid circulation and the partial or full bypassing of cooler 56 during low temperature operation of engine 12. This regulation is achieved by providing in end wall section 18 bypass passageways 58, 60 and 62 and a bypass port 64.
  • the bypass passageways 58 and 60 communicate with dis charge header chamber 52, while bypass passageway 62 communicates with transfer header chamber 48.
  • the bypass port 64 is disposed to communicate inlet port 22 and channel 24 of inlet passageway 30 with bypass passageways 58, 60 and 62.
  • a thermostatically controlled valve 66 is disposed in inlet port 22.
  • the valve 66 may be of any conventional type such as the thermostat manufactured by Standard Thomsen Corp. of Waltham, Massachusetts, and designated Model 4D00l.
  • the valve 66 is constructed and arranged so that its movable valve element 68 is reciprocatable relative to bypass port 64 to and from a seated or closed position on bypass port 64 and an unseated or open position.
  • cooling system 10 In the operation of cooling system 10, with thermostatic valve 66 in the open position as shown in FIG. 2, liquid coolant bypasses outlet passage and port 54 by flowing through bypass passageway 58 and 60 and bypass port 64 into inlet port 22 and, thence, through channel 24 and passageway 30 to the circulating pump. Also, simultaneously with the aforesaid bypass flow, part of the liquid coolant discharging from passageway 40 into transfer header chamber 48, flows through bypass passageway 62 and into inlet port 22, via bypass port 64.
  • This cooler bypass arrangement insures flow of liquid coolant through the engine housing area orzone of highest heat flux by recirculating cooling liquid through passageways 30 and 40 as well as through passagewsys 42 and 44.
  • bypass passageway 64 With bypass port 64closed by thermostatic valve 66, bypass passageway 64 insures that the passageways 30 and 40 adjacent the high heat flux zone of the engine carries the total quantity of cooling liquid flow required in that zone. This assurance of sufficient cooling effect is achieved by-flowing a quantity of liquid through passageways 30 and 40 which is in excess of the flow capacity of passageways 42 and 44 with such excess being passed through bypass passageway 62 and into outlet passage and port 54, via bypass passageway 60.
  • bypass port can be made to communicate with channel 24 instead of outlet passage and port 54.
  • engine 12 is shown as having no liquid cooling flow passageways in the cool zone 70 of the engine housing, the invention is not limited thereto and, without departing from the scope and spirit of this invention, the engine may have cooling flow passages extending around the entire circumference of the engine housing as disclosed in the U.S. Pat. to Jones, No. 3,007,460.
  • the present invention provides a cooling system for a rotary piston, combustion engine, which system provides a relatively large and unrestricted inlet flow passageway into the circulating pump so that the pump can function without cavitation and at optimum capacity and efficiency. It is a system in which more space is made available at the accessory drive end of the engine and in which optimum liquid coolant flow adjacent the area or zone of highest heat flux is maintained with thermostatic valve in the open or closed position. It is also a cooling system where bypass recirculation is achieved wholly within the engine housing when the thermostatic valve is in the open position.
  • a circulating pump having an inlet means for receiving liquid coolant and an outlet means for discharging pressurized liquid coolant to the cooling passageways downstream from the inlet cooling passageway;
  • the circulating pump being disposed at the end of the engine housing opposite from the end of the engine housing where the inlet port is located and with its inlet means in communication with the inlet cooling passageway to draw liquid coolant from the latter;
  • bypass passageway means communicating the cooling passageways downstream from said circulating pump with the inlet port;
  • a temperature responsive valve means disposed in the inlet port to control flow of coolant through the bypass passageway means and into said inlet port and inlet cooling passageway.
  • bypass passageway means includes a bypass passageway which bypasses the valve means and communicates with the outlet port and the cooling passageway downstream from the outlet means of the circulating pump so that a portion of the coolant is conducted directly to the outlet port when the valve means is in a closed position preventing coolant flow into said inlet port through the bycooling passageways extend in substantially parallel repass passageway means.
  • a cooling system for rotary piston, internal combustion engine having a plurality of cooling passageways, including an inletcooling passageway, extending between the end wall sections of the housing and substantially parallelto each other and the axis of rotation of the rotary piston, which cooling passageways are in communication at opposite ends through header chambers in the opposite end wall sections of the housing to provide series flow of cooling fluid therethrough, the cooling system comprising:
  • the cooler means being connected to the inlet cooling passageway at one end thereof in one of the end wall sections of the housing for conducting cooled liquid coolant to the latter and in communication with the cooling passageways to receive heated cooling liquid from the latter;
  • a circulating pump disposed in the other end wall section of the housing to communicate with the end of inlet cooling passageway, opposite from thelatters connection with the cooler means, to draw liquid coolant through the inlet cooling passagey;
  • said circulating pump being in communication with the other plurality of cooling passageways to discharge coolant into the latter;
  • bypass passageway means communicating the said other cooling passageways with the inlet cooling passageway at the said one end wall section of the housing;
  • a temperature responsive valve means disposed in the said one end wall section to control flow of coolant through the bypass passageway means and into said inlet cooling passageway for recirculation through the circulating pump.
  • cooling passageways are interconnected for series flow through header chambers formed in the opposite end wall sections of the engine housing.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
US00245588A 1971-05-10 1972-04-19 Liquid cooling system for rotary piston engines Expired - Lifetime US3743452A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19712123010 DE2123010C3 (de) 1971-05-10 FlUssigkeitsgekUhlte Rotationskolben-Brennkraftmaschine

Publications (1)

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US3743452A true US3743452A (en) 1973-07-03

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US00245588A Expired - Lifetime US3743452A (en) 1971-05-10 1972-04-19 Liquid cooling system for rotary piston engines

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US (1) US3743452A (it)
JP (1) JPS553526B1 (it)
FR (1) FR2139335A5 (it)
GB (1) GB1334477A (it)
IT (1) IT960610B (it)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3832980A (en) * 1972-05-27 1974-09-03 Kawasaki Heavy Ind Ltd Combined hydraulic speed-change, cooling and lubricating system in rotary engine
US3907468A (en) * 1974-05-22 1975-09-23 Gen Motors Corp Rotary engine cooling system
US3935115A (en) * 1973-10-04 1976-01-27 The Dow Chemical Company Coolant for rotary engine
US5275231A (en) * 1992-07-28 1994-01-04 Yoshikazu Kuze Cooling system for an automotive engine
DE102008015031A1 (de) * 2008-03-17 2009-09-24 Wankel Super Tec Gmbh Gehäuse für einen Kreiskolbenmotor und Kreiskolbenmotor
CN104967237A (zh) * 2015-06-29 2015-10-07 蔡勇 转子及转子发动机冷却系统

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5961652U (ja) * 1982-10-18 1984-04-23 日通工株式会社 電話機のスピ−カ用静電気防止カバ−
DE3938331A1 (de) * 1989-11-17 1991-05-23 Wankel Gmbh Kuehlwasserpumpe einer rotationskolbenbrennkraftmaschine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2760468A (en) * 1952-11-01 1956-08-28 Gen Motors Corp Engine cooling system
US3007460A (en) * 1960-03-29 1961-11-07 Curtiss Wright Corp Cooling arrangement for rotary mechanisms
US3384056A (en) * 1966-08-01 1968-05-21 Waukesha Motor Co Temperature control systems for internal combustion engines
US3459161A (en) * 1966-12-03 1969-08-05 Daimler Benz Ag Installation for controlling the cooling medium temperature to a predetermined desired value with an internal combustion engine
DE1916098A1 (de) * 1969-03-28 1970-10-01 Daimler Benz Ag Kuehlsystem fuer Rotationskolben-Brennkraftmaschinen,insbesondere in Trochoidenbauart
US3691999A (en) * 1969-05-31 1972-09-19 Audi Ag Liquid cooled housing for rotary piston engines

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2760468A (en) * 1952-11-01 1956-08-28 Gen Motors Corp Engine cooling system
US3007460A (en) * 1960-03-29 1961-11-07 Curtiss Wright Corp Cooling arrangement for rotary mechanisms
US3384056A (en) * 1966-08-01 1968-05-21 Waukesha Motor Co Temperature control systems for internal combustion engines
US3459161A (en) * 1966-12-03 1969-08-05 Daimler Benz Ag Installation for controlling the cooling medium temperature to a predetermined desired value with an internal combustion engine
DE1916098A1 (de) * 1969-03-28 1970-10-01 Daimler Benz Ag Kuehlsystem fuer Rotationskolben-Brennkraftmaschinen,insbesondere in Trochoidenbauart
US3691999A (en) * 1969-05-31 1972-09-19 Audi Ag Liquid cooled housing for rotary piston engines

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3832980A (en) * 1972-05-27 1974-09-03 Kawasaki Heavy Ind Ltd Combined hydraulic speed-change, cooling and lubricating system in rotary engine
US3935115A (en) * 1973-10-04 1976-01-27 The Dow Chemical Company Coolant for rotary engine
US3907468A (en) * 1974-05-22 1975-09-23 Gen Motors Corp Rotary engine cooling system
US5275231A (en) * 1992-07-28 1994-01-04 Yoshikazu Kuze Cooling system for an automotive engine
DE102008015031A1 (de) * 2008-03-17 2009-09-24 Wankel Super Tec Gmbh Gehäuse für einen Kreiskolbenmotor und Kreiskolbenmotor
DE102008015031B4 (de) * 2008-03-17 2014-10-23 Wankel Super Tec Gmbh Gehäuse für einen Kreiskolbenmotor und Kreiskolbenmotor
CN104967237A (zh) * 2015-06-29 2015-10-07 蔡勇 转子及转子发动机冷却系统

Also Published As

Publication number Publication date
IT960610B (it) 1973-11-30
GB1334477A (en) 1973-10-17
DE2123010A1 (de) 1972-11-16
FR2139335A5 (it) 1973-01-05
JPS553526B1 (it) 1980-01-25
DE2123010B2 (de) 1977-01-27

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