EP0825335B1 - Spritzdüse für die Kolbenkühlung einer Brennkraftmaschine - Google Patents

Spritzdüse für die Kolbenkühlung einer Brennkraftmaschine Download PDF

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Publication number
EP0825335B1
EP0825335B1 EP97110179A EP97110179A EP0825335B1 EP 0825335 B1 EP0825335 B1 EP 0825335B1 EP 97110179 A EP97110179 A EP 97110179A EP 97110179 A EP97110179 A EP 97110179A EP 0825335 B1 EP0825335 B1 EP 0825335B1
Authority
EP
European Patent Office
Prior art keywords
spraying nozzle
nozzle according
combustion engine
internal combustion
diameter
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
EP97110179A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0825335A1 (de
Inventor
Jürgen KLING
Jürgen Poth
Olaf Fiedler
Achim Bauer
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.)
Dr Ing HCF Porsche AG
Original Assignee
Dr Ing HCF Porsche 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
Application filed by Dr Ing HCF Porsche AG filed Critical Dr Ing HCF Porsche AG
Publication of EP0825335A1 publication Critical patent/EP0825335A1/de
Application granted granted Critical
Publication of EP0825335B1 publication Critical patent/EP0825335B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/14—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means with multiple outlet openings; with strainers in or outside the outlet opening
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/0204—Filling
    • F01P11/0209—Closure caps
    • F01P11/0238—Closure caps with overpressure valves or vent valves

Definitions

  • the invention relates to a spray nozzle for the piston cooling of an internal combustion engine according to the genus of the main claim.
  • the pistons In highly loaded internal combustion engines, the pistons often have to be cooled in order to Avoid too high piston temperatures. An excessively high piston temperature has a negative effect on the fatigue strength, especially with light metal materials of the piston. In addition, sometimes occur at very high piston temperatures Problems due to thermal carbon build-up and deposits in the Piston ring grooves on. Further increase with the increase in Piston temperature due to thermal expansion the deviations from the original piston geometry. The areas of highest temperatures of the The piston crown depends on the position of the spark plug, the valve geometry and the ignition timing. The range of highest temperatures is mostly in Exhaust valve area.
  • DE 31 25 835 C2 also discloses a spray nozzle for piston cooling an internal combustion engine is known in which the mouth channel by folding a Pipe is formed, the shape of the mouth channel deviating from the circular shape.
  • a spray nozzle is known with which two or more oil jets are generated that affect different areas of the piston crown.
  • EP 057 790 A1 discloses a nozzle arrangement in which a central bore of several holes are surrounded by a ring.
  • the diameter of the central hole is larger than the diameter of the ring bores, so that a central one when exposed to oil Main jet is formed by a concentric oil jet generated by the ring nozzles is surrounded.
  • the invention is based on the object of a spray nozzle for piston cooling Improve internal combustion engine so that over the entire operating temperature range Internal combustion engine and the lubricating oil and especially at high lubricating oil temperatures targeted, concentrated action on the piston and thus effective cooling is achieved.
  • a spray nozzle should be simple and inexpensive to manufacture and without construction Changes to the internal combustion engine used instead of the generic spray nozzles can be.
  • the diameter d of all mouth channels is substantially the same and the distance a the central axes of the mouth channels to each other is smaller than twice the diameter of the Mouth channels, is a targeted and safe loading of the piston crown even at high Oil temperatures possible.
  • the inventive formation of the mouth channels form with the same total flow rate compared to a conventional spray nozzle even at high Temperatures of the oil and high pressures cause laminar flows within the channel, which is one Prevent the oil jet from fanning out prematurely. It has been shown that through training a beam pattern can be achieved in two closely adjacent mouth channels, in which already about 10 mm up to 30 mm after the nozzle mouth, bundling into a full jet takes place.
  • a particularly good and sharp bundling of the oil jet results when the diameter of the Mouth channels is between 0.8 mm and 1.5 mm.
  • a particularly favorable flow pattern within the mouth channel and one with it accompanying sharp bundling of the emerging oil jet results when the entrance area is expanded conically in the mouth channel.
  • a particularly simple and inexpensive construction of such a spray nozzle is achieved if this has a nozzle end piece with the mouth channels formed therein, which in a sleeve-like carrier component is used.
  • a carrier-like sleeve component can then for example, a check valve can be integrated.
  • the spray nozzle 1 shown in Fig. 1 for the piston cooling of an internal combustion engine consists essentially of a support member 2 and an associated Nozzle end piece 3.
  • the carrier component 2 has a bottom section 4 and one of them outgoing sleeve-shaped section 5.
  • In the bottom section 4 are a Inlet bore 6 and an adjoining valve seat 7 are formed.
  • In the built-in State of the spray nozzle 1 is the supply bore 6 with the lubricating oil circuit Internal combustion engine connected.
  • Inside the sleeve-shaped section 5 is a with the valve seat 7 cooperating valve member 8, which in this Embodiment is designed as a valve ball.
  • the valve member 8 is against Effect of the oil flowing through the supply bore 6 by a spring 9 against the Valve seat 7 pressed and acts as a check valve.
  • the spring 9 is supported on the one hand on the valve member 8 and on the other hand on a circumferential shoulder 10 of the Nozzle end piece 3.
  • the nozzle end piece 3 consists of two cylindrical sections, a first one Section 11 of larger diameter and a second section 12 smaller Diameter. Between the two cylindrical sections 11 and 12 is a conical transition area 13 formed. The nozzle end piece 3 is so in that Carrier component 2 used that the free end face 14 of the first section 11 abuts a circumferential shoulder 15 of the support member 2. By flanging the free edge 16 of the support member, the nozzle end piece is held. The free edge or the flanged section of the free edge 16 is then on the conical Transition 13 at. Starting from the free end face 14 runs in the first cylindrical section 11 a bore 17 which is conical up to the shoulder 10 tapered towards. Two parallel outlet channels 19 extend from the bottom 18 of this bore, 20, which extend into and penetrate the second section 12. The entry area 21, 22 of the two outlet channels 19, 20 is towards the bore 17 expanded conically. The cone angle is approximately in this embodiment 45 °.
  • the two outlet channels 19 and 20 have the in this embodiment same dimensions, i.e. Length and diameter d are the same.
  • the diameter d of the two mouth channels is 1.2 mm in this embodiment. However, it is easily possible to change the diameter depending on the oil pressure, Nozzle length and distance of the piston crown between 0.8 mm and 1.5 mm vary.
  • the distance a between the two outlet channels 19, 20 is in this Embodiment 1.5 mm, but can range between about 1.0 mm and 2.0 mm can be varied. To bundle the two as early as possible to achieve partial beams emerging in a full jet, the distance a should both mouth channels are kept relatively small, i.e. the distance a should be smaller than twice the mouth channel diameter d.
  • valve member 8 is designed as a valve cone. Through this Training can be compared to the spherical design of the valve member 8 achieve a significant reduction in switching hysteresis.
  • the nozzle end piece in Depends on the required oil throughput the available one Oil pressure and the distance of the nozzle end piece from the one to be charged Piston plate also more than two outlet channels can be provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP97110179A 1996-08-17 1997-06-21 Spritzdüse für die Kolbenkühlung einer Brennkraftmaschine Expired - Lifetime EP0825335B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19633167A DE19633167A1 (de) 1996-08-17 1996-08-17 Spritzdüse für die Kolbenkühlung einer Brennkraftmaschine
DE19633167 1996-08-17

Publications (2)

Publication Number Publication Date
EP0825335A1 EP0825335A1 (de) 1998-02-25
EP0825335B1 true EP0825335B1 (de) 2002-09-18

Family

ID=7802868

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97110179A Expired - Lifetime EP0825335B1 (de) 1996-08-17 1997-06-21 Spritzdüse für die Kolbenkühlung einer Brennkraftmaschine

Country Status (5)

Country Link
US (1) US5915345A (ja)
EP (1) EP0825335B1 (ja)
JP (1) JPH1077833A (ja)
KR (1) KR19980018639A (ja)
DE (2) DE19633167A1 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016219857A1 (de) * 2016-10-12 2018-04-12 Bayerische Motoren Werke Aktiengesellschaft Vorrichtung zur Kühlung eines Kolbens einer Hubkolben-Brennkraftmaschine

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Publication number Priority date Publication date Assignee Title
IT1293674B1 (it) * 1997-08-01 1999-03-08 Finmeccanica Spa Ugello per la lubrificazione di organi meccanici.
EP0947285A1 (en) * 1998-03-31 1999-10-06 Senior Engineering Investments AG Automotive engine fluid spray tube apparatus and method for making same
DE19927931A1 (de) * 1999-06-18 2001-01-04 Daimler Chrysler Ag Brennkraftmaschine
SE9902968L (sv) * 1999-08-23 2000-06-19 Scania Cv Ab Anordning för kolvkylning och förfarande för framställning av ett munstycke därtill
DE19943516B4 (de) * 1999-09-11 2017-01-19 Schaeffler Technologies AG & Co. KG Düsenventil
FR2844003B1 (fr) * 2002-09-02 2006-06-16 Bontaz Centre Sa Gicleur a projections multiples pour refroidissement de moteur, et moteurs equipes de tels gicleurs
US20040198464A1 (en) * 2003-03-04 2004-10-07 Jim Panian Wireless communication systems for vehicle-based private and conference calling and methods of operating same
US6863475B2 (en) * 2003-04-30 2005-03-08 Shell Oil Company Apparatus for injecting fluids
DE102004017909A1 (de) * 2004-04-13 2005-11-10 Bayerische Motoren Werke Ag Vorrichtung zur Kühlung von zumindest einem Kolben einer Brennkraftmaschine
US7156056B2 (en) * 2004-06-10 2007-01-02 Achates Power, Llc Two-cycle, opposed-piston internal combustion engine
US7360511B2 (en) 2004-06-10 2008-04-22 Achates Power, Inc. Opposed piston engine
US20060169331A1 (en) * 2004-08-09 2006-08-03 Neto Jose C Fluid jet with noise reducing sleeve
DE112004002968B4 (de) * 2004-09-15 2016-09-15 Ford Otomotiv Sanayi Anonim Sirketi Motor mit einer verbesserten Öldüsenvorrichtung
JP4708837B2 (ja) * 2005-04-13 2011-06-22 株式会社 クニテック オイルジェット
KR100774700B1 (ko) * 2005-12-10 2007-11-08 현대자동차주식회사 체크밸브구조
US8539918B2 (en) * 2009-02-20 2013-09-24 Achates Power, Inc. Multi-cylinder opposed piston engines
US9328692B2 (en) * 2009-02-20 2016-05-03 Achates Power, Inc. Opposed piston engines with controlled provision of lubricant for lubrication and cooling
US8550041B2 (en) * 2009-02-20 2013-10-08 Achates Power, Inc. Cylinder and piston assemblies for opposed piston engines
US9163505B2 (en) 2010-08-16 2015-10-20 Achates Power, Inc. Piston constructions for opposed-piston engines
JP6002657B2 (ja) 2013-02-28 2016-10-05 本田技研工業株式会社 ピストンの冷却装置
WO2014167190A1 (fr) * 2013-04-11 2014-10-16 Bontaz Centre R & D Dispositif de commande de l'alimentation d'un systeme avec un fluide permettant une optimisation de la consommation de fluide
JP6148111B2 (ja) * 2013-08-09 2017-06-14 トヨタ自動車株式会社 オイルジェット
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
GB201519640D0 (en) * 2015-11-06 2015-12-23 Gm Global Tech Operations Inc Piston cooling jet for an internal combustion engine
DE102017223465A1 (de) * 2017-12-20 2019-06-27 Volkswagen Aktiengesellschaft Kolbenkühldüse
WO2023193885A1 (en) * 2022-04-05 2023-10-12 Wärtsilä Finland Oy A nozzle for a cooling arrangement of a piston in an internal combustion piston engine and a cooling arrangement for a piston of an internal combustion piston engine

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GB330095A (en) * 1929-05-02 1930-06-05 James Edwin Tolmie An improved nozzle for fire-extinguishing and like hose pipes
US3423029A (en) * 1966-03-03 1969-01-21 Quigley Co Multiple tube spray discharge nozzle
US3553135A (en) * 1968-07-11 1971-01-05 Ampex Lithium-titanium-manganese copper-microwave ferrite
DD89286A1 (de) * 1970-11-24 1972-04-12 Werner Steinmetz Spritzöl-Kühlvorrichtung
GB1475181A (en) * 1974-02-06 1977-06-01 Perkins Engines Ltd Reciprocating engine having piston oil cooling
DE2853280B2 (de) * 1978-12-09 1981-04-09 Lechler Gmbh & Co Kg, 7012 Fellbach Vollstrahldüse zur Kühlung hochbelasteter Maschinenteile, insbesondere Kolben in Hubkolbenmotoren
JPS57502220A (ja) * 1981-01-23 1982-12-16
DE3125835C2 (de) * 1981-07-01 1985-10-03 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh, 7990 Friedrichshafen Spritzvorrichtung zur Versorgung eines Kolbens mit Kühlflüssigkeit
CS234514B1 (en) * 1983-06-22 1985-04-16 Zdenek Kudelka Equipment for piston spraying by oil
DE4012475A1 (de) * 1989-04-28 1990-10-31 Volkswagen Ag Kolbenkuehlung fuer eine brennkraftmschine
US4979473A (en) * 1989-10-20 1990-12-25 Cummins Engine Company, Inc. Piston cooling nozzle
CA2090330A1 (en) * 1991-09-09 1993-03-10 Willibald G. Berlinger Piston cooling nozzle
EP0577901B1 (en) * 1992-07-10 2000-04-26 International Business Machines Corporation Adaptive equalization system and method

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016219857A1 (de) * 2016-10-12 2018-04-12 Bayerische Motoren Werke Aktiengesellschaft Vorrichtung zur Kühlung eines Kolbens einer Hubkolben-Brennkraftmaschine

Also Published As

Publication number Publication date
KR19980018639A (ko) 1998-06-05
DE19633167A1 (de) 1998-02-19
JPH1077833A (ja) 1998-03-24
US5915345A (en) 1999-06-29
EP0825335A1 (de) 1998-02-25
DE59708245D1 (de) 2002-10-24

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