EP1676989A1 - Moteur à combustion interne avec un dispositif de refroidissement de piston - Google Patents

Moteur à combustion interne avec un dispositif de refroidissement de piston Download PDF

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Publication number
EP1676989A1
EP1676989A1 EP05100002A EP05100002A EP1676989A1 EP 1676989 A1 EP1676989 A1 EP 1676989A1 EP 05100002 A EP05100002 A EP 05100002A EP 05100002 A EP05100002 A EP 05100002A EP 1676989 A1 EP1676989 A1 EP 1676989A1
Authority
EP
European Patent Office
Prior art keywords
crankshaft bearing
supply element
crankshaft
internal combustion
section
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.)
Granted
Application number
EP05100002A
Other languages
German (de)
English (en)
Other versions
EP1676989B1 (fr
Inventor
Ingo Lenz
Carsten Weber
Urban Morawitz
Dietmar Laufenberg
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.)
Ford Global Technologies LLC
Original Assignee
Ford Global Technologies LLC
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
Application filed by Ford Global Technologies LLC filed Critical Ford Global Technologies LLC
Priority to EP05100002A priority Critical patent/EP1676989B1/fr
Priority to US11/324,449 priority patent/US7201118B2/en
Publication of EP1676989A1 publication Critical patent/EP1676989A1/fr
Application granted granted Critical
Publication of EP1676989B1 publication Critical patent/EP1676989B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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
    • F01M2001/086—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating gudgeon pins

Definitions

  • the invention relates to an internal combustion engine with a piston cooling device, which has at least one injection device, which is supplied via at least one supply element with a coolant and lubricant.
  • the US 6,532,912 B2 relates to a piston cooling for internal combustion engines with a crankshaft, a plurality of pistons and a crankcase.
  • the crankcase is subdivided by a plurality of bulkheads into divided regions, wherein a pressure circulation lubrication is integrated in the crankcase, so that lubrication can circulate through the crankcase.
  • the crankcase also has a plurality of longitudinal bores extending through a respective bulkhead of the crankcase generally coaxial with each other and generally parallel to the crankshaft.
  • the piston cooling system has a plurality of bores, which are each introduced into the respective bulkhead and are connected to the pressure circulation lubrication.
  • the piston cooling system has a plurality of spray nozzles, each of which is mounted in an associated longitudinal bore and directed so that lubricant is injected onto an underside of the piston, which are so connected to a respective bore that each spray nozzle with the pressure circulation lubrication connected is.
  • Each spray nozzle is designed as a compact rotary part and has a transverse bore with opposite open ends. The open ends are each closed with a stopper.
  • the spray nozzle also has two symmetrical to the center of the injection holes, the lubricant flows through the inlet bore to get into the closed transverse bore, and is sprayed out of the spray holes.
  • the inlet bore is aligned with the bore of the respective bulkhead in which the spray nozzle is mounted.
  • US 4,010,718 is a piston internal combustion engine with a cylinder block contained at least one cylinder, at least one in the associated cylinder up and down movable piston, a crankcase, a rotatably mounted in the crankcase in at least one bearing crankshaft and disclosed with at least one connecting rod for connecting the crankshaft to the associated pistons.
  • the crankcase is provided with a lubricating oil passage.
  • the crankcase has in each case between a main bearing and the associated piston with a standing in connection with the lubricating oil passage bore.
  • a tubular nozzle assembly is installed in a precisely predetermined position fixed in the bore of the crankcase.
  • the nozzle assembly has an internal cavity in communication with the lubricating oil passage.
  • the nozzle assembly also has at least one nozzle channel which has been formed in a precisely predetermined position prior to installation of the nozzle assembly into the associated bore on the nozzle assembly.
  • US 5,533,472 relates to a ⁇ lspritzdüsenkolbenkühlanssen for an internal combustion engine with two adjacent cylinders in which reciprocally movable piston are mounted.
  • a crankshaft space is disposed between the cylinders, with a crankshaft having at least one lubrication bearing disposed in the crankshaft space.
  • the cylinder block has pins between the adjacent cylinders to support the crankshaft bearing.
  • An oil supply passage is inserted in the cylinder block to guide lubricating oil to the journal and the bearing.
  • a groove is formed in the cylinder block with at least a portion of the groove connected to the crankpin to receive lubricating oil from the supply line.
  • a first passage is formed in the cylinder block which extends between the adjacent cylinders substantially parallel to the crankshaft and located above the crankshaft journal.
  • a second channel is inserted in the cylinder block which extends between the groove and the first channel.
  • the oil jet piston cooling system includes a spray assembly having an inlet end and an outlet end opposite thereto. Through the inlet end oil enters the spray nozzle, which is ejected through the outlet end.
  • the spray nozzle is mounted in the second channel so that its outlet end is adjacent to the groove to receive oil from the spigot so that its outlet end is open to the first channel to produce oil streams flowing upwardly through the first channel and the cylinders squirt against the underside of the adjacent pistons.
  • US 5,533,472 also relates to an internal combustion engine having a cylinder block which accommodates reciprocally movable pistons within a piston cylinder.
  • a connecting rod connects the piston to a crankshaft.
  • the cylinder block has a crankshaft receptacle below the piston and a crankshaft journal for supporting a crankshaft bearing and an oil feed line on one side of the piston cylinder.
  • the oil supply line is connected to a groove and the crankshaft journal and the crankshaft bearing to provide a channel through the bearing to the crankshaft.
  • a channel extends from the oil groove to the crankshaft receptacle and is provided with an oil spray nozzle which injects oil onto an underside of the piston.
  • the oil spray nozzle has an element which is inserted into the channel extending from the oil groove to Kurbelwellenaug fortune.
  • the spray nozzle has a lower area with outputs and an upper area with inputs.
  • a projection of the element is designed such that it sits in the oil groove.
  • the projection has a width so that it is snugly received by the oil groove.
  • piston oil spray nozzles are positioned below the cylinder liners for cooling the pistons in the cylinder block. These piston oil spray nozzles require a pressure oil supply, which is realized by means of a separate longitudinal bore in the cylinder block. This means a considerable amount of design and manufacturing overhead.
  • the invention has for its object to improve an internal combustion engine with a piston cooling device with simple means such that they can be produced more cheaply and manufacturing technology easier.
  • the object is achieved in that the supply element is arranged in a module which is composed of a crankshaft bearing structure element and a crankshaft bearing cap, wherein the injection device is associated with the crankshaft bearing cap, and wherein a crankshaft bearing shell in the region of the supply element has a through hole, so that the cooling and lubricant through the module is feasible over the supply element to both the spray device and a crankshaft.
  • the supply element By means of the supply element according to the invention, the supply of the spray device with the coolant and lubricant is taken directly by the main crankshaft bearing, which means that the direct supply of coolant and lubricant of the crankshaft main bearing is shared.
  • a combined injector / crankshaft main bearing oil supply is provided.
  • the module is assembled from the crankshaft bearing structural member and the crankshaft bearing cap and bolted to the cylinder block.
  • the module supports the crankshaft.
  • the module thus has a double function. First, the crankshaft is stored in this. On the other hand, the module takes over the integrated in this supply element both the lubrication of the crankshaft and the supply of the sprayer with the coolant and lubricant.
  • the supply element is arranged in cross-section with a first portion in the crankshaft bearing structure element and with a, in the first section merging second portion in the crankshaft bearing cap.
  • the supply element is configured only with a single portion which is arranged in the crankshaft bearing cap or a crankshaft bearing cover composite.
  • the supply element is limited on the one hand with its outer wall of an inner wall portion of the module and on the other hand with its inner wall of an outer wall portion of the crankshaft bearing shell and that the spraying device is associated with the crankshaft bearing cap in the region of the supply element.
  • the supply element can be supplied with the coolant and lubricant, in particular with oil, it may be expedient for the purposes of the invention, when the supply element with its first portion with a in this opening coolant and lubricant channel is connected, which is introduced into the crankshaft bearing structure element.
  • the crankshaft bearing structural element may be, for example, a lead frame.
  • the coolant and lubricant passage may open in the supply member without being guided by the crankshaft bearing structural member.
  • the supply element is designed with its first section in cross-section substantially triangular with an oriented to its outer wall rounded tip, wherein a base leg is formed according to a curvature of the crankshaft bearing shell.
  • the supply element extends with its second wall with its outer wall in a first region in cross-section preferably straight, wherein the first region merges into a second region whose outer wall is configured according to a curvature of the crankshaft bearing shell.
  • the coolant and lubricant can reach both the spray device and the crankshaft, it is favorable in the context of the invention, when the supply element in cross section is partially guided by about 40 to 60%, preferably by about 45% of the circumference of the crankshaft bearing shell , wherein the passage opening is expediently arranged in the region of the second region of the second section of the supply element in the crankshaft bearing shell. It is also conceivable, however, to guide the supply element fully or more or less partially around the crankshaft bearing shell.
  • the spraying device is designed as a spray nozzle, which is accommodated in a receiving bore of the crankshaft bearing cap.
  • the spray nozzle is secured against axial rotation, but also against loosening from the receiving bore, it is advantageously provided that the spray nozzle is positively frictionally connected via a retaining element with the crankshaft bearing cap.
  • the spray nozzle but also be positively received in the bore, so that the spray nozzle sufficiently against rotation or Loosening is secured.
  • the spray nozzle is firmly bonded to the crankshaft bearing cap.
  • a welded connection or adhesive bond can be provided.
  • the coolant and lubricant is injected via the spray nozzle to a piston to be cooled.
  • the spraying device is integrated as at least one directional and calibrated injection bore in the crankshaft bearing cap itself.
  • two spray holes are integrated into the crankshaft bearing cap, which are arranged at an angle to each other.
  • the spray holes take over the function of spray nozzles and can be advantageously integrated in any position and orientation in the crankshaft bearing cap.
  • the supply of coolant and lubricant is of course via the supply element according to the invention, but can also be done via conventional channels and / or supply elements.
  • both with spray nozzle and with spray holes it is favorable in the context of the invention, when a module, for example, is used with a lead frame structure whose crankshaft bearing cap is above a crankshaft axis.
  • FIG. 1 shows a section of an internal combustion engine with a piston cooling device 1.
  • the piston cooling device 1 has at least one injection device 2.
  • the spray device 2 is supplied via at least one supply element 3 with a coolant and lubricant.
  • the supply element 3 is arranged in a module 4, which is composed of a crankshaft bearing structure element 6 and a crankshaft bearing cap 7. Seen in cross-section, the supply element 3 is arranged with a first section 8 in the crankshaft bearing structure element 6 and with a second section 9 merging into the first section 8 in the crankshaft bearing cover 7.
  • the supply element 3 has an outer wall 10 and an inner wall 11 opposite thereto.
  • the outer wall 10 is formed by an inner wall portion 12 of the crankshaft bearing structure element 6 and the crankshaft bearing cap 7.
  • the inner wall 11 of the supply element 3 is formed by an outer wall section 13 of a crankshaft bearing shell 14.
  • the supply element 3 is limited on the one hand with its outer wall 10 of the inner wall portion 12 of the crankshaft bearing structure element 6 and the crankshaft bearing cap 7 and on the other hand with its inner wall 11 of the outer wall portion 13 of the crankshaft bearing shell 14 and configured channel-like.
  • the spraying device 2 is assigned to the crankshaft bearing cap 7 in the region of the supply element 3.
  • the crankshaft bearing shell 14 has a passage opening 16 in the region of the supply element 3, preferably in the region of its second section 9. This allows the cooling and Lubricant over the supply element 3 are guided both to the spray device 2 and to a crankshaft 17.
  • the module 4 is screwed to a cylinder block, not shown, and supports the crankshaft 17th
  • the supply element 3 is connected with its first section 8 with an opening into this coolant and lubricant channel 18.
  • the coolant and lubricant channel 18 is introduced into the crankshaft bearing structure element 6 and connected to an oil gallery, not shown.
  • the coolant and lubricant channel 18 is guided, as viewed in cross section, below a crankshaft main axis Y, to the first section 8 of the supply element 3.
  • the coolant and lubricant preferably oil
  • the coolant and lubricant channel 18 is preferably machined into the crankshaft bearing structure element 6, but can also be cast in during its production, for example in its casting production, and / or introduced manually with suitable aids.
  • the supply element 3 is designed with its first section 8 seen in cross-section substantially triangular with an oriented to its outer wall 10, rounded tip.
  • a base leg 19 of the first section 8 is formed according to a curvature of the crankshaft bearing shell 14.
  • the supply element 3 is seen with its outer wall in a first region 21 in cross-section preferably straight running in the crankshaft bearing cap 7 is introduced, wherein the first region 21 merges into a second region 22 which is configured according to a curvature of the crankshaft bearing shell 14 ,
  • the supply element 3 viewed in cross-section, is guided by approximately 40 to 60%, preferably by approximately 45%, of the circumference of the crankshaft bearing shell 14.
  • the crankshaft bearing shell 14 is composed of two pieces of an upper shell part 23 and a lower shell part 24.
  • the passage opening 16 is preferably arranged in the upper shell part 23 in the region of the second region 22 of the second section 9 of the supply element 3.
  • the passage opening 16 is arranged offset relative to a zenith of the crankshaft bearing shell 14 in the clockwise direction by approximately 20 °.
  • the passage opening 16 may be positioned in any position in the region of the supply element 3, wherein a sufficient passage of the coolant and lubricant for a sufficient lubrication of the crankshaft 17 should be ensured.
  • crankshaft bearing cap 7 is connected to the crankshaft bearing structural element 6.
  • corresponding holes (screw whistle) 26 are introduced both in the crankshaft bearing structure element 6 and in the crankshaft bearing cap 7, so that the crankshaft bearing structure element 6 can be screwed to the crankshaft bearing cap 7.
  • the module 4 is connected to a cylinder block, not shown, preferably screwed.
  • the spraying device 2 is designed as an oil spray nozzle 27 in the exemplary embodiment illustrated in FIG.
  • a matching receiving bore 28 is introduced into the crankshaft bearing cap 7.
  • the oil spray nozzle 27 is positively frictionally connected to the crankshaft bearing cap 7 via a retaining element 29.
  • the holding member 29 is seen in the embodiment shown in cross-section plate-shaped and has two through holes 31 and 32, wherein the oil spray nozzle 27 is guided through the through hole 31 and a corresponding screw 33 through the through hole 32, wherein the screw 33 in a corresponding thereto Threaded hole 34 is screwed into the crankshaft bearing cap 7, so that the Oil spray nozzle 27 is sufficiently secured against rotation and release from the receiving bore 28.
  • Figure 2 shows the protruding from the crankshaft bearing cap 7 injection end 36 of the oil spray nozzle 27.
  • injection end 36 directed injection holes are introduced, so that oil spray jets 37 are sprayed onto adjacent piston 38.
  • FIGS. 3 and 4 A further embodiment of the spraying device 2 is shown in FIGS. 3 and 4.
  • the spraying device 2 is formed from directional and calibrated injection bores 39, which are integrated directly into the crankshaft bearing cap 7.
  • the injection bores 39 are arranged at an acute angle relative to the crankshaft main axis Y.
  • the injection bores 39 are continuously guided through the crankshaft bearing cap 7 and open into the second region 22 of the second section 9 of the supply element 3.
  • the oil spray jets 37 are sprayed through the respective spray hole 39 or through the spray nozzle 27 past a cylinder track 41 to the respective piston 38 in order to cool it.
  • Figures 5 to 13 show different embodiments of the supply element 3 with the associated coolant and lubricant channel 18. Although the embodiments of Figures 5 to 13, the embodiment with the Oil spray nozzle 27 show, it is of course possible to use these embodiments also in the embodiment with calibrated and directed spray holes 39.
  • the supply element 3 is arranged entirely with only one section in the crankshaft bearing cover 7 or a crankshaft bearing cover composite.
  • the supply element 3 is partially guided by approximately 10 to 20% of the circumference of the crankshaft bearing shell 14.
  • the supply element 3 extends in this case with respect to a zenith of the crankshaft bearing shell 14 in the clockwise direction seen from about 40 ° beyond the zenith, and is slightly shorter than the second region 22 of Figures 1 and 3 configured.
  • the coolant and lubricant channel 18 is introduced as a transverse bore 42 to a longitudinal bore 43 for oil supply back into the Kurbelellwellenlagerdeckel 7 and the Kurbelwellenlagerdeckelverbund in which the longitudinal bore 43 is introduced.
  • the longitudinal bore 43 is configured round in cross-section, and arranged above the crankshaft main axis Y.
  • the supply element 3 is based on the embodiment of Figure 5 designed slightly longer, and starts approximately at about 80 ° relative to the zenith of the crankshaft bearing shell 14 and corresponds in its extension in approximately the second region 22 Figures 1 and 3.
  • the coolant and lubricant channel 18 is configured as a transverse bore 44 and connected to a longitudinal bore 46 for oil supply. Both the transverse bore 44 and the longitudinal bore 46 are introduced into the Kurbelellwellenlagerdeckel 7 and the Kurbelwellenlagerdeckelverbund
  • the longitudinal bore 46 is seen in cross-section configured round and seen in cross section within the bore (screw pipe) 26.
  • the supply element 3 is designed in its extension corresponding to the second region 22 with a partial section of the first region 21.
  • the supply element 3 extends in this embodiment, approximately from the crankshaft main axis Y, which are also referred to as parting plane can.
  • the coolant and lubricant channel 18 is connected as a transverse channel 47 with a longitudinal bore 48 to oil supply.
  • the longitudinal bore 48 is seen in cross section round, and slightly above the crankshaft main axis Y in the bore (screw whistle) 26 is arranged.
  • the embodiment of Figure 8 has a longitudinal channel 49 for oil supply, which is frusto-conical in cross-section. With its base side 51 of the longitudinal channel 49 is arranged approximately congruent to the crank main axis Y and extends with its opposite frusto-conical surface 52 in the upward direction.
  • the longitudinal channel 49 is arranged in mirror image to the arrangement of Figure 8, and extends with its frustoconical surface 52 opposite.
  • the supply element 3 is configured identically to the exemplary embodiments in FIGS. 7 to 9.
  • the transverse channel 47 is connected to a longitudinal channel 53, which is oval in cross-section and is arranged with its halves in equal parts above or below the crankshaft main axis Y (parting plane).
  • the longitudinal channel 53 is thus arranged with one half in the crankshaft bearing cap 7 or the crankshaft bearing cover composite and with its other half in the crankshaft bearing structure element 6.
  • the transverse channel 47 is connected to a longitudinal bore 54, which, viewed in cross-section, has a round configuration and is arranged in the crankshaft bearing structural element 7.
  • the coolant and lubricant channel 18 or the respective transverse bores or channels 42, 44, 47 are arranged entirely in the crankshaft bearing cap 7 or the crankshaft bearing cap composite.
  • the coolant and lubricant channel 18 and its transverse channel 47 according to the embodiment of Figure 12 is arranged both in the crankshaft bearing cap 7 and the crankshaft bearing cover composite and in the crankshaft bearing structure element 6.
  • the transverse channel 47 is divided by means of the crankshaft main axis (dividing plane) Y into two equal halves.
  • the longitudinal bore 54 is designed and arranged according to the embodiment of Figure 11.
  • the transverse channel 47 is arranged entirely in the crankshaft bearing structure element 6.
  • the longitudinal bores or channels exemplified in FIGS. 5 to 13 can be guided both through the bore (screw pipe) 26 and also arranged outside.
  • the transverse channel can be arranged in the parting plane, wherein, of course, any meaningful shape and position is conceivable.
  • the transverse channel is arranged in the parting plane, since in this advantageous arrangement, this can already be introduced during the production, in particular during the production by casting, without the need for additional reworking.
  • the individual different in cross-sectional geometric configurations of the respective channels or holes are not limited to those described and combined in a meaningful way.
  • the respective longitudinal and transverse bores can be produced by casting as channels.
  • the supply element 3 with its outer wall 10 with its outer wall 10 in a first region 21 in cross-section can preferably be inclined by 2 to 3 ° in the direction of the screw pipe 26.
  • modules 4 In the preferred embodiments, only one module 4 is shown and described in each case. Of course, in multi-cylinder internal combustion engines, a corresponding number of modules 4 can be used, which preferably form a composite.
  • crankshaft bearing structure elements 6 in engines with several cylinder banks, in particular at a cylinder angle of 180 °.
  • the function of the thereby omitted crankshaft bearing cap 7 or composite is adopted in this case by the second crankshaft bearing structural element.
  • the function of the omitted crankshaft bearing cover or composite can also be taken over by the first crankshaft bearing structural element 6.
EP05100002A 2005-01-03 2005-01-03 Moteur à combustion interne avec un dispositif de refroidissement de piston Expired - Fee Related EP1676989B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP05100002A EP1676989B1 (fr) 2005-01-03 2005-01-03 Moteur à combustion interne avec un dispositif de refroidissement de piston
US11/324,449 US7201118B2 (en) 2005-01-03 2006-01-03 Piston-cooling arrangement for an internal combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05100002A EP1676989B1 (fr) 2005-01-03 2005-01-03 Moteur à combustion interne avec un dispositif de refroidissement de piston

Publications (2)

Publication Number Publication Date
EP1676989A1 true EP1676989A1 (fr) 2006-07-05
EP1676989B1 EP1676989B1 (fr) 2011-11-23

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EP (1) EP1676989B1 (fr)

Cited By (4)

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Publication number Priority date Publication date Assignee Title
EP1826388A1 (fr) * 2006-02-28 2007-08-29 HONDA MOTOR CO., Ltd. Système de refroidissement de piston de moteur à combustion interne
US7448355B2 (en) 2006-03-27 2008-11-11 Honda Motor Co., Ltd. Integrated power unit including split crankcase with reinforced fastening arrangement, and vehicle including same
US7458359B2 (en) 2006-10-23 2008-12-02 Honda Motor Co., Ltd. Internal combustion engine having crankcase with stress-relieving wall structure
DE102007058796A1 (de) * 2007-12-06 2009-06-10 GM Global Technology Operations, Inc., Detroit Ölkanalanordnung

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DE102004017909A1 (de) * 2004-04-13 2005-11-10 Bayerische Motoren Werke Ag Vorrichtung zur Kühlung von zumindest einem Kolben einer Brennkraftmaschine
DE102004019630A1 (de) * 2004-04-22 2005-11-17 Wacker Construction Equipment Ag Ölversorgung für einen Verbrennungsmotor
GB201103261D0 (en) * 2011-02-25 2011-04-13 Mahle Int Gmbh A bearing arrangement
AT514804B1 (de) * 2013-12-10 2015-04-15 Steyr Motors Gmbh Verbrennungskraftmaschine mit Ölkanälen
US9470136B2 (en) * 2014-03-06 2016-10-18 Achates Power, Inc. Piston cooling configurations utilizing lubricating oil from a bearing reservoir in an opposed-piston engine
FR3047769B1 (fr) * 2016-02-17 2019-05-31 Bontaz Centre R & D Gicleur d'huile de fabrication simplifiee
US11333140B2 (en) * 2019-06-11 2022-05-17 Caterpillar Inc. Cooling block for multi-cylinder air compressor
US11248515B2 (en) * 2019-08-02 2022-02-15 Transportation Ip Holdings, Llc Piston cooling jet system
US11927127B1 (en) * 2023-04-11 2024-03-12 S&S Cycle, Inc. Dual spray piston cooling jet device

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US5533472A (en) 1995-07-31 1996-07-09 Chrysler Corporation Oil jet nozzle for an internal combustion with reciprocating pistons
FR2745329A1 (fr) * 1996-02-23 1997-08-29 Renault Circuit de lubrification pour moteur a combustion interne
EP0982479A1 (fr) * 1998-08-22 2000-03-01 Cummins Engine Company, Ltd. Commande de débit pour un gicleur d'huile
JP2003074346A (ja) * 2001-08-31 2003-03-12 Kubota Corp ピストン冷却装置
US6532912B2 (en) 2000-05-17 2003-03-18 Man Nutzfahrzeuge Ag Piston cooling system for an internal combustion engine

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US6742481B2 (en) * 2002-09-23 2004-06-01 General Motors Corporation Piston cooling oil system with windage tray
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US4010718A (en) 1974-02-06 1977-03-08 Perkins Engines Limited Reciprocating piston engines having piston oil cooling
US5533472A (en) 1995-07-31 1996-07-09 Chrysler Corporation Oil jet nozzle for an internal combustion with reciprocating pistons
FR2745329A1 (fr) * 1996-02-23 1997-08-29 Renault Circuit de lubrification pour moteur a combustion interne
EP0982479A1 (fr) * 1998-08-22 2000-03-01 Cummins Engine Company, Ltd. Commande de débit pour un gicleur d'huile
US6532912B2 (en) 2000-05-17 2003-03-18 Man Nutzfahrzeuge Ag Piston cooling system for an internal combustion engine
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1826388A1 (fr) * 2006-02-28 2007-08-29 HONDA MOTOR CO., Ltd. Système de refroidissement de piston de moteur à combustion interne
US7322318B2 (en) 2006-02-28 2008-01-29 Honda Motor Co., Ltd. Cooling system for an internal combustion engine, and engine incorporating same
US7448355B2 (en) 2006-03-27 2008-11-11 Honda Motor Co., Ltd. Integrated power unit including split crankcase with reinforced fastening arrangement, and vehicle including same
US7458359B2 (en) 2006-10-23 2008-12-02 Honda Motor Co., Ltd. Internal combustion engine having crankcase with stress-relieving wall structure
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EP1676989B1 (fr) 2011-11-23
US20060169224A1 (en) 2006-08-03

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