Insulated oil cooled piston assembly

Claim 2

An oil cooled piston assembly for a diesel engine, said assembly comprising a body member having an outer generally cylindrical ring belt section connected near its upper edge with a supporting wall integral with a piston pin connecting section, said wall and said ring belt section defining a cooling oil space for receiving cooling oil to cool said ring belt section and said wall, and a separate combustion chamber defining member secured to said body member and having a hot wall with one side adapted to be exposed to engine combustion gases in a combustion chamber and an opposite side extending opposite and generally parallel to said body member supporting wall, said walls cooperating and being spaced apart intermediate their ends to define an enclosed insulating air gap that limits heat flow from the combustion chamber defining member to the oil cooled wall of the body member, said air gap having throughout the major portion of its extent a thickness within a range of about 20% less than to 20% more than the value determined by the formula ##EQU4## where: b=air gap thickness ν=kinematic viscosity of the air in the gap β=the coefficient of thermal expansion of the air in the gap r=radius of crank to which the piston is connected ω=selected crank rotational speed in radians per second ΔT=differential temperature across the air gap at said selected speed to minimize the combined effects of conductive and convective heat transfer and thus provide a maximum insulating effect through maintenance of an essentially stagnant air condition within the gap.

Claim 3

An oil cooled piston assembly for an internal combustion engine, said assembly comprising a body member having an outer generally cylindrical ring belt section connected near its upper edge with a depending cup shaped supporting wall integral with a piston pin connecting section below said wall, said wall and said ring belt section defining an annular cooling oil cavity therebetween for receiving cooling oil to cool said ring belt section, said wall defining inwardly thereof a cup shaped recess closed at the bottom by said piston pin connecting section and adapted to receive an axially symmetrical insert, and a separate combustion bowl member received within said recess, said bowl member having a depending columnar section with an open bottom received against the closed bottom of said recess, a central bowl section extending inwardly from the upper edge of the columnar section and closing the top thereof to enclose a central chamber not directly cooled by coolant in said cooling oil cavity and a peripheral bowl section extending outwardly and upwardly from said columnar section upper edge, said peripheral bowl and columnar sections together defining a continuous outwardly and upwardly flared inner wall generally parallel to said body member supporting wall, said walls being in engagement at their lower ends and spaced apart intermediate their ends to define an insulating air gap to limit heat loss from the combustion bowl member to the oil cooled wall of the body member, said air gap having throughout the major portion of its extent a thickness within a range of about 20% less than to 20% more than the value determined by the formula ##EQU5## where: b=air gap thickness ν=kinematic viscosity of the air in the gap β=the coefficient of thermal expansion of the air in the gap r=radius of crank to which the piston is connected ω=selected crank rotational speed in radians per second ΔT=differential temperature across the air gap at said selected speed to minimize the combined effects of conductive and convective heat transfer and thus provide a maximum insulating effect through maintenance of an essentially stagnant air condition within the gap.

Claim 4

An oil cooled piston assembly for an internal combustion engine, said assembly comprising a body member having an outer generally cylindrical ring belt section connected near its upper edge with a depending cup shaped supporting wall integral with a piston pin connecting section below said wall, said wall and said ring belt section defining an annular cooling oil cavity therebetween for receiving cooling oil to cool said ring belt section, said wall defining inwardly thereof a cup shaped recess closed at the bottom by said piston pin connecting section and adapted to receive an axially symmetrical insert, and a separate combustion bowl member received within said recess, said bowl member having a depending columnar section with an open bottom received against the closed bottom of said recess, a central bowl section extending inwardly from the upper edge of the columnar section and closing the top thereof to enclose a central chamber not directly cooled by coolant in said cooling oil cavity and a peripheral bowl section extending outwardly and upwardly from said columnar section upper edge, said peripheral bowl and columnar sections together defining a continuous outwardly and upwardly flared inner wall generally parallel to said body member supporting wall, said walls being in engagement at their lower ends and spaced apart intermediate their ends to define an insulating air gap to limit heat loss from the combustion bowl member to the oil cooled wall of the body member, said air gap having throughout the major portion of its extent a thickness within a range of about 20% less than to 20% more than the value determined by the formula ##EQU5## where: b=air gap thickness ν=kinematic viscosity of the air in the gap β=the coefficient of thermal expansion of the air in the gap r=radius of crank to which the piston is connected ω=selected crank rotational speed in radians per second ΔT=differential temperature across the air gap at said selected speed to minimize the combined effects of conductive and convective heat transfer and thus provide a maximum insulating effect through maintenance of an essentially stagnant air condition within the gap.