US2800119A - Arrangement for cooling the piston of internal combustion engines - Google Patents

Arrangement for cooling the piston of internal combustion engines Download PDF

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Publication number
US2800119A
US2800119A US506329A US50632955A US2800119A US 2800119 A US2800119 A US 2800119A US 506329 A US506329 A US 506329A US 50632955 A US50632955 A US 50632955A US 2800119 A US2800119 A US 2800119A
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Prior art keywords
oil
piston
nozzle
cooling
engine
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Expired - Lifetime
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US506329A
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Schmidl Rudolf
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MAN AG
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MAN Maschinenfabrik Augsburg Nuernberg AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/06—Arrangements for cooling pistons
    • F01P3/08—Cooling of piston exterior only, e.g. by jets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • Thisinvention relatee-to anarrangement for-cooling thepisto'n of internal. combustion engines; andmore parpiston head, by means of a throwing device, preferablyar nozzle, under action of the full pressure of the oil in the lubricating system.
  • the device-for branching off cooling oil from the-main oiling circuit and-casting it against the pistonihead is provided with acheck valve which iscontrolledoby the oil pressure of the main oiling circuit, independently of the relief pressure valve normally arranged in the. oilingcircuit, in such. away that in case of a decrease of..this pressure to .aspredetermined lower limit, e. .g.-,.the idle run pressure of the oil pump, the discharge of-oilfrom the spraying device is. automatically prevented.
  • Fig. l is an axial section through an injection type internal combustion engine with a nozzle for the piston cooling jet connected to the main oiling circuit, the nozzle with nozzle holder being partly shown in a perspective view;
  • FIG. 2 is a side view, partly in section, showing the nozzle and the nozzle holder on a larger scale.
  • the engine is a conventional injection-type internal combustion engine in which the combustion chamber 11 is provided in the head of the piston 1 jointed to a piston rod 15 and reciprocating in a cylinder 12 having a cover 13 in which the fuel nozzle system 14 is accommodated.
  • a nozzle holder 6 supporting a nozzle 3 through which lubricating oil is sprayed against the inner wall of the piston head 2.
  • the oil is delivered from a sump 16 through oil pump 17 into a main oiling circuit 19 from which parallelly connected lines 4 and 20 lead, respectively, to a cooling oil branch circuit and lubricating oil branch branch circuit for the lubrication points of the engine.
  • the oil is returned to sump 16 either by drainage from the crankcase and/or through return 21. In case of an excess of pressure at the relief-pressure valve 18, the same will permit a portion of the oil to return directly to the sump 16, through a pipe 22, for keeping the pressure in the main oiling circuit within the normal limits.
  • branch cooling oil circuit 4 contains the nozzle holder 6 accommodating a non-return valve 7 which is acted upon by a compression spring 8.
  • the lubricating oil is fed from the branch cooling oil duct 4 connected to main oiling circuit pipe 19,
  • a cleaning opening 10 at the left hand end of the nozzle holder is normally closed by a plug 23.
  • the tension of the spring 8 is adapted insuch a way that the same normally is overcome by the pressure prevailing in 'the oil duct 4, so that the valve 7 in normal operation of the engine remains always open, for spraying oil through the nozzle 3 against the piston head 2.
  • Valve 7 Only when the oil pressure falls below a predetermined value which has been adjusted by the tension of the spring 8, the Valve 7 will be closed by the spring pressure which now preponderates, whereby the supply of oil to the nozzle 3 is checked and lubricating oil can flow only tothe remaining-lubricating points, and more particularly to the bearingsof' the engine. 7
  • valve 7 before the spray nozzle 3 has nothing' to do With the'relief pressure valve 18 arranged in the lubricating oil circuit and serving to return a surplus of lubrieating oil to the sump 16, and it is quite independent of said relief pressure valve as to its function.
  • said opening and closing means comprising a spring automatically responsive to the oil pressure in said main oiling circuit.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Description

y 1957 SCHMIDL 2,800,119
ARRANGEMENT coouue THE PISTON OF INTERNAL COMBUSTION mamas Filed May 5, 1955 INVENTOR United States Pate ARRANGEMENT :FoR cooLlNG THE PISTON- or INTERNAL COMBUSTION ENGINES I Rudolfl-SchmidL Numberg, Germany, assignonto Maschinenfabrik Augsburg-Numberg. A; G., Numberg, Germany:
Application-May 5, 1955, Serial No. 506,329
z-Claims.v (Cl. 12341.35)
Thisinventionrelatee-to anarrangement for-cooling thepisto'n of internal. combustion engines; andmore parpiston head, by means of a throwing device, preferablyar nozzle, under action of the full pressure of the oil in the lubricating system.
In high-duty diesel engines tor trucksa jet of oil is continuously sprayed against the piston .headin order to .con-
trol the temperature of the piston, and 'especia'lly'of the piston head. Normallythe oililis:sprayed into each of the cylinders through a nozzle whichds supplied .with oil from the main oiling circuit. The nozzle tends-to become obstructed by impurities of the oil. In order to avoid this, the diameter of the nozzle had to be made larger than re quired for the proper purpose of the nozzle. Thus, for instance, it has been found by practical experiences that the diameter of the nozzle should not be less than 1.5 mms. With such a nozzle diameter, however, the amount of fuel flowing oil through all of the nozzles of a multicylinder engine is very considerable. For instance, with an 8-cylinder engine in case of the above mentioned nozzle diameter of 1.5 mms., the total nozzle cross section for all cylinders would be about 14 mm. Referring this to a single symbolic substitute nozzle this would correspond to a nozzle diameter of about 3.5 mms. However, it has been found by practical measurements that the entire lubricating oil throughput of the engine is adapted only to the cross section of a symbolic substitute nozzle of about 4.5 mms. diameter, which shows that the share of lubricating oil flowing out through the spray nozzle is a very considerable one. Hence a sufiicien-tly large lubricating oil pressure must be accumulated in order that all oil consuming points of the engine are supplied with a sufficient amount of oil. This again requires a sufficiently high delivery of the oil circulation pump. Such large oil circulation pumps, however, are disadvantageous with a view to the efiiciency of the engine, since they absorb a considerable amount of energy which must be supplied by the engine. On the other hand, if the oil circulation pump is too small in relation to the oil spraying nozzles for cooling the piston, the lubricating oil pressure with slow or idle run of the engine will break down nearly to zero because the amount of oil which is supplied is decreasing proportional to the speed of the engine while the cross section of the nozzles remains unchanged.
Hereat the drawback exists that during slow or idle run of the engine the lubricating oil, following the path of lowest resistance, is discharged mainly from the nozzles having a relatively large bore while for instance the bearings will be supplied with a very small portion of the lubricating oil only, and that at a point of time where there is no actual necessity for cooling the piston or the piston head, respectively.
ice
Itwill he -understood that similar conditions may occur where inplaceof nozzles any other device is used for sprayingthemil against: the pistonhead and where for constructional reasons the throughput of oil for cooling the piston must be made larger than normally required.
It is an object of the presentinvention to provide means for 'avoidingthese drawbacks.-
More particularly, it is anobject of theinvention to control the share of lubricating oil branched 01$ for. cooling-thepistonor.thehead of. the piston, in dependence upon the'speed of the engine.
With these and further objects in view, accordingto the. presentinventiomthedevice-for branching off cooling oil from the-main oiling circuit and-casting it against the pistonihead .is provided with acheck valve which iscontrolledoby the oil pressure of the main oiling circuit, independently of the relief pressure valve normally arranged in the. oilingcircuit, in such. away that in case of a decrease of..this pressure to .aspredetermined lower limit, e. .g.-,.the idle run pressure of the oil pump, the discharge of-oilfrom the spraying device is. automatically prevented. Where" a'nozzleis used as .an injecting device, in per se knownmanner, a non-return valve is arranged inthe duct ,to=,the nozzle, said non-return valve responding to the pressure prevailing in themai-noiling circuit at slow or idle run .ofthe engine, in such away that the oil in this conditiomofipperation is prevented from issuing from the In-this manneritis: possible totdesign-the oil pump for a much smaller output without in any way reducing the elfective cooling capacity at the piston.
Other and further objects, features and advantages of the invention will be pointed out hereinafter and appear in the appended claims forming part of the application.
In the accompanying drawings a now preferred embodiment of the invention is shown by way of illustration and not by way of limitation.
Fig. l is an axial section through an injection type internal combustion engine with a nozzle for the piston cooling jet connected to the main oiling circuit, the nozzle with nozzle holder being partly shown in a perspective view;
'Fig. 2 is a side view, partly in section, showing the nozzle and the nozzle holder on a larger scale.
Similar reference numerals denote similar parts in the two figures.
Referring now to the drawing, and first to Fig. 1, it will be seen that the engine is a conventional injection-type internal combustion engine in which the combustion chamber 11 is provided in the head of the piston 1 jointed to a piston rod 15 and reciprocating in a cylinder 12 having a cover 13 in which the fuel nozzle system 14 is accommodated. Provided in the crank case is a nozzle holder 6 supporting a nozzle 3 through which lubricating oil is sprayed against the inner wall of the piston head 2.
The oil is delivered from a sump 16 through oil pump 17 into a main oiling circuit 19 from which parallelly connected lines 4 and 20 lead, respectively, to a cooling oil branch circuit and lubricating oil branch branch circuit for the lubrication points of the engine. The oil is returned to sump 16 either by drainage from the crankcase and/or through return 21. In case of an excess of pressure at the relief-pressure valve 18, the same will permit a portion of the oil to return directly to the sump 16, through a pipe 22, for keeping the pressure in the main oiling circuit within the normal limits.
As shown in Fig. 2 in greater detail, branch cooling oil circuit 4 contains the nozzle holder 6 accommodating a non-return valve 7 which is acted upon by a compression spring 8. The lubricating oil is fed from the branch cooling oil duct 4 connected to main oiling circuit pipe 19,
through a non-return valve 7 and the channelS in the nozzle holder 6, as indicated by the arrows 9. A cleaning opening 10 at the left hand end of the nozzle holder is normally closed by a plug 23. The tension of the spring 8 is adapted insuch a way that the same normally is overcome by the pressure prevailing in 'the oil duct 4, so that the valve 7 in normal operation of the engine remains always open, for spraying oil through the nozzle 3 against the piston head 2. Only when the oil pressure falls below a predetermined value which has been adjusted by the tension of the spring 8, the Valve 7 will be closed by the spring pressure which now preponderates, whereby the supply of oil to the nozzle 3 is checked and lubricating oil can flow only tothe remaining-lubricating points, and more particularly to the bearingsof' the engine. 7
The valve 7 before the spray nozzle 3 has nothing' to do With the'relief pressure valve 18 arranged in the lubricating oil circuit and serving to return a surplus of lubrieating oil to the sump 16, and it is quite independent of said relief pressure valve as to its function.
It will be appreciated that the oil pressure will fall below the above mentioned critical value for instance during slow or idle run of the engine. In this case, however, the amount of heat transmitted to the piston is relatively small, so that it is not necessary for the piston head to be sprayed with cooling oil in this Working condition.
While the invention has been described in detail with respect to a now preferred example and embodiment'of the invention it will be understood by those skilled in the art after understanding the invention that various changes and modifications may be made without departing from the spirit and scope of the invention and it is intended,
therefore, to cover all such changes and modifications in the appended claims.
I claim:
1. In an internal combustion engine such as a high output Diesel engine having a main oiling circuit, an oil circulating pump in said main circuit, at least one lubrication branch circuit leading from said main circuit to the engine lubrication points, and at least one piston cooling branch circuit leading from the main circuit to a spray nozzle for spraying cooling oil into the hollow interior of a piston, both branch circuits being connected in parallel to said main oiling circuit, respectively, the improvement comprising a spray nozzle in said piston cooling branch circuit having an opening of a size to provide a flow resistance to the passage of oil less than the flow resistance in the lubricating branch circuit at engine idling speeds, a check valve connected to said nozzle, and means for opening said valve under the pressure of the main oiling circuit during normal engine running speeds, but for closing said valve during low running or engine idling speeds. V
2. In an internal combustion engine as in claim 1, said opening and closing means comprising a spring automatically responsive to the oil pressure in said main oiling circuit.
References Cited in the file of this patent UNITED STATES PATENTS 1,992,339 Winslow Feb. 26, 1935 FOREIGN PATENTS 833,880 Germany Mar. 13, 1952 1037,0224 France Apr. 29, 1953
US506329A 1955-05-05 1955-05-05 Arrangement for cooling the piston of internal combustion engines Expired - Lifetime US2800119A (en)

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Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3065743A (en) * 1961-02-09 1962-11-27 Int Harvester Co Internal combustion engine lubricating system and temperature regulating means for the pistons thereof
US3144095A (en) * 1962-04-27 1964-08-11 Outboard Marine Corp Oiling system
US3152333A (en) * 1961-10-18 1964-10-06 Thompson Ramo Wooldridge Inc Gas assisted zero gravity lubrication system
US3181514A (en) * 1963-11-21 1965-05-04 Continental Aviat & Eng Corp Piston construction
US3189010A (en) * 1963-11-21 1965-06-15 Continental Aviat & Eng Corp Piston for internal combustion engine
US3221722A (en) * 1964-01-03 1965-12-07 Continental Aviat & Eng Corp Piston
US3709109A (en) * 1969-11-07 1973-01-09 Kloeckner Humboldt Deutz Ag Piston cooling arrangement for a reciprocating piston internal combustion engine with an injection nozzle
US3768252A (en) * 1971-01-09 1973-10-30 Mtu Friedrichshafen Gmbh Cylinder crankcase assembly for dual crankshaft multi-cylinder engine
US3785457A (en) * 1970-10-08 1974-01-15 Daimler Benz Ag Internal combustion engine
US3817058A (en) * 1971-09-22 1974-06-18 V Lombardi Cylinder and dial construction for knitting machines
US4011032A (en) * 1975-03-21 1977-03-08 Audi Nsu Auto Union Aktiengesellschaft System for liquid cooling of a rotor or a rotary mechanism
US4114571A (en) * 1975-10-16 1978-09-19 Max Ruf Means for controlling the oil cooling of the piston of a piston engine
FR2388990A1 (en) * 1977-04-28 1978-11-24 Brown Tractors Ltd INTERNAL COMBUSTION ENGINE LUBRICATION SYSTEM
US4129108A (en) * 1975-09-30 1978-12-12 Elsbett L Piston for internal combustion engines
US4142484A (en) * 1975-09-05 1979-03-06 Daimler-Benz Aktiengesellschaft Piston for internal combustion engine
US4206726A (en) * 1977-07-18 1980-06-10 Caterpillar Tractor Co. Double orifice piston cooling nozzle for reciprocating engines
US4508065A (en) * 1983-03-21 1985-04-02 General Motors Corporation Piston cooling oil delivery tube assembly
US4862838A (en) * 1988-06-07 1989-09-05 Stanadyne Automotive Corp. Crankcase oil spray nozzle for piston cooling
US4876990A (en) * 1988-06-07 1989-10-31 Stanadyne Automotive Corp. Spray nozzle assembly for piston cooling
US4901679A (en) * 1988-09-30 1990-02-20 Stanadyne Automotive Corp. Spray nozzle assembly for piston cooling
US4936417A (en) * 1988-06-24 1990-06-26 Mtu Friedrichshafen Gmbh Lubricating system which includes a splash cooling of the pistons of an internal-combustion engine
US4995346A (en) * 1989-06-28 1991-02-26 Sharon Manufacturing Company Oil jet piston cooler
US5533472A (en) * 1995-07-31 1996-07-09 Chrysler Corporation Oil jet nozzle for an internal combustion with reciprocating pistons
US20030005893A1 (en) * 2001-07-04 2003-01-09 Christophe Bontaz Piston cooling nozzle
US20050072476A1 (en) * 2003-09-09 2005-04-07 Neto Jose Correa Fluid jet for providing fluid under pressure to a desired location
US20060169331A1 (en) * 2004-08-09 2006-08-03 Neto Jose C Fluid jet with noise reducing sleeve
US7198020B1 (en) 2006-03-13 2007-04-03 Steven G Beddick Lubrication systems and methods for an internal combustion engine
US20080210314A1 (en) * 2004-12-21 2008-09-04 Jose Correa Neto Fluid jet with noise reducing sleeve
US20090124441A1 (en) * 2004-09-10 2009-05-14 Schaeffler Kg Housing of a tensioning system with an intergrated spray nozzle
US20100001103A1 (en) * 2007-09-07 2010-01-07 Jose Correa Neto Piston cooling jet with tracking ball orifice
CN103174539A (en) * 2011-12-21 2013-06-26 川崎重工业株式会社 Cooling structure of piston in engine
US20140091161A1 (en) * 2012-09-29 2014-04-03 Toyota Jidosha Kabushiki Kaisha Piston cooling jet
US20140216371A1 (en) * 2013-02-06 2014-08-07 Briggs & Stratton Corporation Spray cooled oil system for an internal combustion engine
US8955474B1 (en) 2011-04-14 2015-02-17 Patrick J. Derbin Closed loop electronic control for the reduction of soot produced in diesel, gasoline and alternative-fueled engines
WO2021224903A1 (en) * 2020-05-03 2021-11-11 Yaacobi Amnon Method and system for controlling the temperature of an engine
DE10318070C5 (en) 2003-04-17 2022-06-23 Volkswagen Ag Device and method for lubricating and cooling gear drives

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1992339A (en) * 1929-01-30 1935-02-26 Catherine B Winslow Lubricating system for internal combustion engines
DE833880C (en) * 1949-11-01 1952-03-13 Willy Lehmann Additional lubrication for working piston
FR1037028A (en) * 1950-09-09 1953-09-14 Piston fitted with a dip tube cooling device for fast running internal combustion engines

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1992339A (en) * 1929-01-30 1935-02-26 Catherine B Winslow Lubricating system for internal combustion engines
DE833880C (en) * 1949-11-01 1952-03-13 Willy Lehmann Additional lubrication for working piston
FR1037028A (en) * 1950-09-09 1953-09-14 Piston fitted with a dip tube cooling device for fast running internal combustion engines

Cited By (47)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3065743A (en) * 1961-02-09 1962-11-27 Int Harvester Co Internal combustion engine lubricating system and temperature regulating means for the pistons thereof
US3152333A (en) * 1961-10-18 1964-10-06 Thompson Ramo Wooldridge Inc Gas assisted zero gravity lubrication system
US3144095A (en) * 1962-04-27 1964-08-11 Outboard Marine Corp Oiling system
US3181514A (en) * 1963-11-21 1965-05-04 Continental Aviat & Eng Corp Piston construction
US3189010A (en) * 1963-11-21 1965-06-15 Continental Aviat & Eng Corp Piston for internal combustion engine
US3221722A (en) * 1964-01-03 1965-12-07 Continental Aviat & Eng Corp Piston
US3709109A (en) * 1969-11-07 1973-01-09 Kloeckner Humboldt Deutz Ag Piston cooling arrangement for a reciprocating piston internal combustion engine with an injection nozzle
US3785457A (en) * 1970-10-08 1974-01-15 Daimler Benz Ag Internal combustion engine
US3768252A (en) * 1971-01-09 1973-10-30 Mtu Friedrichshafen Gmbh Cylinder crankcase assembly for dual crankshaft multi-cylinder engine
US3817058A (en) * 1971-09-22 1974-06-18 V Lombardi Cylinder and dial construction for knitting machines
US4011032A (en) * 1975-03-21 1977-03-08 Audi Nsu Auto Union Aktiengesellschaft System for liquid cooling of a rotor or a rotary mechanism
US4142484A (en) * 1975-09-05 1979-03-06 Daimler-Benz Aktiengesellschaft Piston for internal combustion engine
US4129108A (en) * 1975-09-30 1978-12-12 Elsbett L Piston for internal combustion engines
US4114571A (en) * 1975-10-16 1978-09-19 Max Ruf Means for controlling the oil cooling of the piston of a piston engine
FR2388990A1 (en) * 1977-04-28 1978-11-24 Brown Tractors Ltd INTERNAL COMBUSTION ENGINE LUBRICATION SYSTEM
US4204487A (en) * 1977-04-28 1980-05-27 David Brown Tractors Limited Internal combustion engines
US4206726A (en) * 1977-07-18 1980-06-10 Caterpillar Tractor Co. Double orifice piston cooling nozzle for reciprocating engines
US4508065A (en) * 1983-03-21 1985-04-02 General Motors Corporation Piston cooling oil delivery tube assembly
US4862838A (en) * 1988-06-07 1989-09-05 Stanadyne Automotive Corp. Crankcase oil spray nozzle for piston cooling
US4876990A (en) * 1988-06-07 1989-10-31 Stanadyne Automotive Corp. Spray nozzle assembly for piston cooling
US4936417A (en) * 1988-06-24 1990-06-26 Mtu Friedrichshafen Gmbh Lubricating system which includes a splash cooling of the pistons of an internal-combustion engine
US4901679A (en) * 1988-09-30 1990-02-20 Stanadyne Automotive Corp. Spray nozzle assembly for piston cooling
US4995346A (en) * 1989-06-28 1991-02-26 Sharon Manufacturing Company Oil jet piston cooler
US5533472A (en) * 1995-07-31 1996-07-09 Chrysler Corporation Oil jet nozzle for an internal combustion with reciprocating pistons
US20030005893A1 (en) * 2001-07-04 2003-01-09 Christophe Bontaz Piston cooling nozzle
US6672262B2 (en) * 2001-07-04 2004-01-06 Bontaz Centre Piston cooling nozzle
DE10318070C5 (en) 2003-04-17 2022-06-23 Volkswagen Ag Device and method for lubricating and cooling gear drives
US20050072476A1 (en) * 2003-09-09 2005-04-07 Neto Jose Correa Fluid jet for providing fluid under pressure to a desired location
US7152623B2 (en) 2003-09-09 2006-12-26 Metaldyne Company, Llc Fluid jet for providing fluid under pressure to a desired location
US7766035B2 (en) 2003-09-09 2010-08-03 Metaldyne, Llc Fluid jet for providing fluid under pressure to a desired location
US20060169331A1 (en) * 2004-08-09 2006-08-03 Neto Jose C Fluid jet with noise reducing sleeve
US8202184B2 (en) * 2004-09-10 2012-06-19 Schaeffler Technologies AG & Co. KG Housing of a tensioning system with an intergrated spray nozzle
US20090124441A1 (en) * 2004-09-10 2009-05-14 Schaeffler Kg Housing of a tensioning system with an intergrated spray nozzle
US20080210314A1 (en) * 2004-12-21 2008-09-04 Jose Correa Neto Fluid jet with noise reducing sleeve
US7708026B2 (en) 2004-12-21 2010-05-04 Metaldyne, Llc Fluid jet with noise reducing sleeve
US7198020B1 (en) 2006-03-13 2007-04-03 Steven G Beddick Lubrication systems and methods for an internal combustion engine
US8397749B2 (en) 2007-09-07 2013-03-19 Metaldyne Company Llc Piston cooling jet with tracking ball orifice
US20100001103A1 (en) * 2007-09-07 2010-01-07 Jose Correa Neto Piston cooling jet with tracking ball orifice
US8955474B1 (en) 2011-04-14 2015-02-17 Patrick J. Derbin Closed loop electronic control for the reduction of soot produced in diesel, gasoline and alternative-fueled engines
CN103174539A (en) * 2011-12-21 2013-06-26 川崎重工业株式会社 Cooling structure of piston in engine
US20130160724A1 (en) * 2011-12-21 2013-06-27 Kawasaki Jukogyo Kabushiki Kaisha Cooling structure of piston in engine
CN103174539B (en) * 2011-12-21 2015-05-06 川崎重工业株式会社 Cooling structure of piston in engine
US20140091161A1 (en) * 2012-09-29 2014-04-03 Toyota Jidosha Kabushiki Kaisha Piston cooling jet
US9010282B2 (en) * 2012-09-29 2015-04-21 Taiho Kogyo Co., Ltd. Piston cooling jet
US20140216371A1 (en) * 2013-02-06 2014-08-07 Briggs & Stratton Corporation Spray cooled oil system for an internal combustion engine
US9784151B2 (en) * 2013-02-06 2017-10-10 Briggs & Stratton Corporation Spray cooled oil system for an internal combustion engine
WO2021224903A1 (en) * 2020-05-03 2021-11-11 Yaacobi Amnon Method and system for controlling the temperature of an engine

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