EP1273774B1 - Spritzdüse für Kolbenkühlung - Google Patents

Spritzdüse für Kolbenkühlung Download PDF

Info

Publication number
EP1273774B1
EP1273774B1 EP20020356115 EP02356115A EP1273774B1 EP 1273774 B1 EP1273774 B1 EP 1273774B1 EP 20020356115 EP20020356115 EP 20020356115 EP 02356115 A EP02356115 A EP 02356115A EP 1273774 B1 EP1273774 B1 EP 1273774B1
Authority
EP
European Patent Office
Prior art keywords
piston
bore
cooling
downstream
nozzle
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.)
Revoked
Application number
EP20020356115
Other languages
English (en)
French (fr)
Other versions
EP1273774A1 (de
Inventor
Christophe Bontaz
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.)
Bontaz Centre SA
Original Assignee
Bontaz Centre SA
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=8865247&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1273774(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Bontaz Centre SA filed Critical Bontaz Centre SA
Publication of EP1273774A1 publication Critical patent/EP1273774A1/de
Application granted granted Critical
Publication of EP1273774B1 publication Critical patent/EP1273774B1/de
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

Links

Images

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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/265—Plural outflows
    • Y10T137/2663—Pressure responsive

Definitions

  • the present invention relates to the cooling nozzles of the pistons of an internal combustion engine, for projecting a cooling fluid such as oil against the piston bottom, that is to say against the outer piston face to the explosion chamber, or in a piston gallery.
  • the piston cooling nozzles usually used are inserts attached to the crankcase and communicating with a coolant supply port.
  • the position of the nozzle is precisely determined to achieve a jet of cooling fluid directed to a specific area of the piston bottom or the piston gallery.
  • the cooling nozzles generally include a valve, for inhibiting the circulation of cooling fluid until the pressure of the cooling circuit has exceeded a determined threshold value.
  • Spray structures are generally used, the valve of which is made by a ball, pushed by a compression spring towards a seat to close a passage of cooling fluid. These structures are short and compact.
  • the inventors have found that the valve cooling nozzles used until now function properly and are satisfactory for a limited time, after which time appear phenomena of wear that disturb the sealing of the valve and its proper operation.
  • the correct operating time is shorter as the nominal pressure of the coolant in the cooling lines is high.
  • the wear mainly modifies the opening characteristics of the valve, ie the fluid pressure necessary to trigger it: at nine, the valve opens at a correct nominal pressure; after wear, the valve opens at a lower pressure, up to half the correct nominal pressure, therefore below the idle speed of the engine. This results in a disturbance of the general pressure of the fluid in the engine.
  • the invention results from the observation that the phenomena of wear are inevitable because of the very structure of the ball valve: under high pressure, there are phenomena of oscillation and vibration of the ball, phenomena that cause wear defects.
  • the valve comprises a piston pushed against a seat by a spring and sliding in an axial bore communicating with a radial fluid passage.
  • the structure is long and cumbersome, because the opening of the valve requires to move and guide the piston downstream of the radial fluid passage.
  • the problem proposed by the present invention is to design a new valve sprinkler structure, capable of functioning properly for a significantly longer period, in particular without significant wear.
  • a piston valve does not have the disadvantages of oscillation and vibration of the ball valves, so that satisfactory use can be achieved for a much longer period of time.
  • Another problem that the invention proposes to solve is to reduce the size of the nozzle in the engine cylinder.
  • the piston valves of JP 07 317519 A lead to a relatively large size, and in particular a relatively large length downstream of the valve outlet orifices for guiding the piston. Too long a length downstream of the outlet ports of the valve is a risk of collision with the rotating elements of the engine such as the crankshaft or against the weight of crankshaft.
  • the invention aims to reduce the total length of the nozzle, and in particular the nozzle length protruding into the engine cylinder downstream of the outlet radial fluid passage structure and outlet tube.
  • the invention provides a piston cooling nozzle of an internal combustion engine, having a penetrating nozzle body shaped to engage a bore of the engine and to receive a coolant fluid arriving through said bore, having an internal valve for modulating the fluid flow rate as a function of its pressure, and having a radial fluid passage outlet structure in the nozzle body and outlet tube, adapted to transmit the cooling fluid exiting the inner valve and for directing it against the bottom of the engine piston to be cooled;
  • the internal valve comprises a piston, having a downstream section with a cylindrical lateral guide surface engaged longitudinally in a guide bore integral with the nozzle body, having a closure head oriented upstream in the direction of flow of the cooling fluid to come wear selectively against an annular sealing seat secured to the nozzle body and traversed by the cooling fluid
  • the inner valve comprises a helical compression spring, axially engaged between a downstream surface integral with the nozzle body and a downstream surface of the piston for biasing the piston upstream against the annular sealing seat.
  • Such a structure has a great endurance, a great stability, which reduces the oscillations and very substantially reduces the phenomena of wear.
  • the guide bore in which the piston slides is essentially inside an upstream section of the nozzle body, upstream of the radial fluid passage, and fluid conduction passages axially conduct the fluid. from the downstream of the annular sealing seat to the radial fluid passage as soon as the piston moves away from the annular closure seat, so that, in the open state of the internal valve, the piston is essentially in upstream of the radial fluid passage.
  • downstream piston section comprises a downstream coaxial housing in which engages and is guided the upstream end portion of the coil compression spring.
  • the nozzle body comprises a through axial bore, in which is engaged without play and held in position a tubular liner with axial bore, a downstream section forms the guide bore receiving the downstream piston section, the jacket tubular having an internal intermediate shoulder forming the annular sealing seat, at least one radial hole being provided in the tubular liner wall immediately downstream of the annular sealing seat to conduct the fluid radially towards one or more peripheral passages provided between the outer surface of the tubular liner and the surface of the axial through bore of the nozzle body, said peripheral passages being adapted to axially drive the coolant from the radial hole (s) to the radial fluid passage in the jet body .
  • the piston is upstream of the radial fluid outlet passage.
  • peripheral passage or passages are made by a larger diameter axial through-bore section, while the tubular liner has a substantially constant outer diameter leaving an annular intermediate space through which the cooling fluid flows.
  • the tubular liner is made of sintered steel, while the piston is made of steel. This considerably promotes sliding between the piston and the liner, thus reducing the phenomena of wear and the risk of galling.
  • the piston comprises, between its downstream section with cylindrical lateral guide surface and the closure head, an external annular recess defining, with the wall of the guide bore, an annular housing communicating by radial holes.
  • piston piston with an axial piston bore open downstream in the axial through bore of the body which conducts the cooling fluid to the radial fluid passage in the nozzle body. In this way, in the open state of the valve, the piston is clearly upstream of the radial fluid outlet passage.
  • the annular sealing seat may be an annular ring reported in the axial bore passing through the nozzle body.
  • a piston cooling nozzle for an internal combustion engine comprises a nozzle body 1, an internal valve 2, and an outlet structure 3 adapted to transmit the cooling fluid exiting the valve. and to direct it in jet at least against the bottom of a piston to cool.
  • the nozzle body 1 comprises a penetrating portion 4, shaped to engage in a bore of the engine and to receive a cooling fluid arriving through said bore of the engine.
  • the nozzle body 1 has a projecting portion 5, intended to protrude into the engine cylinder and to carry the outlet structure 3.
  • the internal valve 2 comprises a piston 6, having a downstream section 7 with a lateral cylindrical guide surface 8 engaged longitudinally in a groove. guide bore 9 secured to the nozzle body 1.
  • the piston 6 comprises a closure head 10, directed upstream in the direction of flow of the cooling fluid to come selectively to bear against an annular closure seat 11 secured to of the nozzle body 1 and having a seat bore 12 to be traversed by the cooling fluid.
  • the internal valve 2 further comprises a helical compression spring 13, engaged axially between a downstream bearing 14 secured to the nozzle body 1 and a downstream surface 15 of the piston 6, to bias the piston 6 upstream against the annular seat of the piston. shutter 11.
  • the outlet structure 3 comprises at least one radial fluid passage 17 in the nozzle body 1, and at least one outlet tube 18 having a first end fitted into the corresponding radial fluid passage 17.
  • the piston 6 slides in the guide bore 9 inside an upstream section 16 of nozzle body 1, upstream of the radial fluid passage 17, between a valve closing position and an opening position of valve. In the valve opening position, the piston 6 remains essentially upstream of the radial fluid passage 17.
  • the piston sliding sealingly in the guide bore 9 is opposed a priori to the passage of fluid between the annular sealing seat 11 and the radial fluid passage 17.
  • the invention provides, in either of the illustrated embodiments, fluid conduction passages leading the fluid axially from the downstream of the annular sealing seat 11 to the radial fluid passage 17 as soon as the piston s
  • the fluid conduction passages will be described hereinafter and have different structures in either of the illustrated embodiments.
  • the downstream section 7 of the piston 6 has a coaxial housing downstream 19 in which engages and is guided the part Upstream end 20 of the compression coil spring 13.
  • the nozzle body 1 comprises a through axial bore 21, along the axis I-I of the nozzle body 1, in which the piston 6 slides axially.
  • a tubular liner 22 is engaged without play and held in position in the axial through bore 21, in the protruding portion 5 of the nozzle, being engaged between a downstream plug 39 and a ring 40.
  • the tubular liner 22 comprises an axial bore 23, a downstream portion of which forms the guide bore 9 receiving the downstream portion of the piston 6.
  • the tubular liner 22 comprises an internal intermediate shoulder forming the annular sealing seat 11.
  • At least one radial hole 24 is provided in the wall of the tubular liner 22, immediately downstream of the annular sealing seat 11, for radially conducting the fluid to one or more peripheral passages provided between the outer surface of the tubular liner 22. and the surface of the axial through bore 21 of the nozzle body 1.
  • the peripheral passages 25 are adapted to axially drive the cooling fluid from the radial hole (s) 24 to the radial fluid passage 17 in the nozzle body 1 .
  • the piston 6 can be arranged permanently upstream of the radial fluid passage 17 in the nozzle body 1, and the protruding portion 5 can thus have a reduced volume.
  • peripheral passages 25 are made by a through-bore axial bore section 21 of larger diameter, while the tubular liner 22 has a substantially constant outer diameter, leaving an annular intermediate space by which flows the cooling fluid.
  • the tubular liner 22 may advantageously be made of sintered steel, while the piston 6 is made of steel. This results in a very low coefficient of friction, and good lubrication between the piston 6 and the tubular liner 22, facilitating piston movements without wear and reducing the risk of galling.
  • This first embodiment further promotes the stability of the valve, in that the valve is subjected upstream to the cooling fluid pressure, while it is subjected downstream only to the air pressure and to the return force of the spring.
  • the valve is either open when the fluid pressure is greater than the spring force, or closed in the opposite case, but never vibrates between the two positions.
  • the piston 6 comprises, between its downstream section 7 with lateral cylindrical guide surface 8 and the closure head 10, an external annular recess 26 defining, with the wall of the guide bore 9, an annular housing communicating by radial piston holes 27 with an axial bore of piston 28 open downstream in the axial through bore 21 of the body which conducts the cooling fluid to the radial fluid passage 17 in the body of jet 1.
  • This second structure also makes it possible to place the piston 6 permanently upstream of the radial fluid passage 17 in the nozzle body 1, by ensuring the axial conduction of the fluid from the annular sealing seat 11 to the radial fluid passage 17 .
  • vent 29 downstream of the housing containing the compression coil spring 13, the vent 29 allowing the passage of air into and out of the spring housing during the movements of the piston 6.
  • the vent 29 is formed in the downstream plug 39.
  • the annular sealing seat 11 is an annular ring 30, attached in the axial through bore 21 of the nozzle body.
  • the cooling fluid arrives through the upstream end 31 in a bore of the engine block.
  • the pressure of the cooling fluid is greater than a predetermined threshold, the fluid pushes the piston 6 against the return force exerted by the compression coil spring 13, so that the cooling fluid can pass between the shutter head 10 and the annular shutter seat 11.
  • the cooling fluid passes radially through the radial holes 24, then axially along the peripheral passages 25, to reach the radial fluid passage 17 and exit through the outlet tubes 18.
  • the cooling fluid passes between the annular sealing seat 11 and the sealing head 10, is distributed in the outer annular recess 26, passes radially towards the center by the radial holes piston 27, then moves axially in the axial piston bore 28 and in the axial through bore 21 of the body which conducts the cooling fluid to the radial fluid passage 17 and the outlet tube 18.
  • Figure 7 illustrates the implantation of a nozzle according to the invention in an internal combustion engine.
  • the figure illustrates a motor part, comprising a motor half-cylinder.
  • the nozzle 32 is attached to the wall of the cylinder housing 33, inside the engine, to take cooling fluid circulating in a cooling pipe 34 and to project the cooling fluid into the cylinder motor against the bottom 35 of the engine piston 36, that is to say against the face of the engine piston which is external to the explosion chamber 37.
  • the penetrating portion 4 of the nozzle 32 is engaged in a corresponding bore of the cylinder housing 33, communicating with the cooling pipe 34.
  • the nozzle is thus fixed by any known means, for example force-fitted or screwed into the corresponding bore of the Cylinder case 33.
  • the protruding portion 5 of the nozzle 32 protrudes into the interior of the engine cylinder.
  • An internal combustion engine can thus advantageously comprise piston cooling nozzles according to the invention, as described above, fixed in the piston chamber or chambers and adapted to each project the cooling fluid in a concentrated jet against the bottom of the piston. 'A piston.
  • the present invention is not limited to the embodiments that have been explicitly described, but includes the various variants thereof.

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)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Compressor (AREA)
  • Nozzles (AREA)
  • Surgical Instruments (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Medicinal Preparation (AREA)

Claims (8)

  1. Düse (32) zum Kühlen des Kolbens (36) eines Motors mit innerer Verbrennung, mit einem Düsenkörper (1), der einen eindringenden Abschnitt (4) hat, der angepaßt ist, um in eine Bohrung des Motors einzugreifen und ein Kühlfluid zu empfangen, das durch die genannte Bohrung ankommt, mit einer internen Klappe (2) zum Modulieren des Durchflußes des Fluides in Abhängigkeit von dessen Druck, und mit einer Ausgangsstruktur (3) mit einer radialen Passage (17) für Fluid in dem Düsenkörper (1) und mit einem Ausgangsrohr (18), das ausgebildet ist, um das Kühlfluid, das von der inneren Klappe (2) austritt, weiterzuleiten und um es in einem Strahl zumindest gegen den Boden (35) des Kolbens (36) des zu kühlenden Motors zu leiten, wobei die innere Klappe (2) einen Kolben (6) aufweist, der einen stromabwärtigen Abschnitt (7) mit zylindrischer Seitenfläche (8) zum Führen aufweist, die in Längsrichtung gleitend in eine Führungsbohrung (9) eingreift, die in dem Düsenkörper (1) angebracht ist, mit einem Verschlußkopf (10), der stromaufwärts in Richtung der Strömung des Kühlfluides ausgerichtet ist, um wahlweise gegen einen ringförmigen Verschlußsitz (11) zur Anlage zu kommen, der einstückig mit dem Düsenkörper (1) ist und von dem Kühlfluid durchquert wird, und wobei die innere Klappe (2) eine schraubenförmige Druckfeder (13) enthält, die axial zwischen einem stromabwärtigen Anschlag (14) in dem Düsenkörper (1) und einer stromabwärtigen Fläche (15) des Kolbens (6) eingreift, um den Kolben (6) stromaufwärts gegen den ringförmigen Verschlußsitz (11) zu drücken, dadurch gekennzeichnet, daß die Führungsbohrung (9), in der der Kolben (6) gleitet, im wesentlichen im Inneren eines stromaufwärtigen Abschnittes (16) des Düsenkörpers (1) ist, stromaufwärts der radialen Fluidpassage (17), und daß Passagen (24, 25 ; 26, 27, 28) zum Leiten des Fluides das Fluid axial von der stromabwärtigen Seite des ringförmigen Verschlußsitzes (11) bis zur radialen Fluidpassage (17) leiten, sobald der Kolben (6) sich von dem ringförmigen Verschlußsitz (11) fortbewegt, derart, daß sich im geöffneten Zustand der inneren Klappe (2) der Kolben (6) im wesentlichen stromaufwärts der radialen Fluidpassage (17) befindet.
  2. Düse zum Kühlen nach Anspruch 1, dadurch gekennzeichnet, daß der stromabwärtige Abschnitt (7) des Kolbens (6) einen koaxialen stromabwärtigen Abschnitt (19) aufweist, in welchen ein stromaufwärtiges Endteil (20) der schraubenförmigen Druckfeder (13) eingreift und darin geführt ist.
  3. Düse zum Kühlen nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet,
    daß der Düsenkörper (1) eine axiale Durchgangsbohrung (21) aufweist, in die eine röhrenförmige Hülse (22) mit axialer Bohrung (23) spielfrei eingreift und in der sie in Position gehalten ist, wobei ein stromabwärtiger Abschnitt derselben die Führungsbohrung (9) bildet, die den stromabwärtigen Abschnitt des Kolbens (6) aufnimmt, wobei die röhrenförmige Hülse (22) eine innere zwischenliegende Schulter aufweist, die den ringförmigen Verschlußsitz (11) bildet, wobei mindestens ein radiales Loch (24) in der Wand der röhrenförmigen Hülse (22) unmittelbar stromabwärts des ringförmigen Verschlußsitzes (11) vorgesehen ist, um das Fluid radial in Richtung zu einer oder mehreren Umfangspassagen (25) zu leiten, die zwischen der äußeren Fläche der röhrenförmigen Hülse (22) und der Fläche der axialen Durchgangsbohrung (21) des Düsenkörpers (1) vorgesehen sind, wobei die genannten Umfangspassagen (25) angepaßt sind, um das Kühlfluid axial von dem oder den radialen Löchern (24) bis zur radialen Fluidpassage (17) in dem Düsenkörper (1) zu leiten.
  4. Düse zum Kühlen nach Anspruch 3, dadurch gekennzeichnet, daß die Umfangspassage oder die Umfangspassagen (25) durch einen Abschnitt der axialen Durchgangsbohrung (21) mit größerem Durchmesser gebildet ist bzw. gebildet sind, während die röhrenförmige Hülse (22) einen Außendurchmesser aufweist, der im wesentlichen konstant ist und einen ringförmigen Zwischenraum läßt, durch den das Kühlfluid fließt.
  5. Düse zum Kühlen nach einem der Ansprüche 3 oder 4, dadurch gekennzeichnet,
    daß die röhrenförmige Hülse (22) aus gesintertem Stahl ist, während der Kolben (6) aus Stahl ist.
  6. Düse zum Kühlen nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet,
    daß der Kolben (6) zwischen seinem stromabwärtigen Abschnitt (7) mit zylindrischer Seitenfläche (8) zum Führen und dem Verschlußkopf (10) eine ringförmige äußere Ausnehmung (26) hat, die mit der Wand der Führungsbohrung (9) einen ringförmigen Sitz bildet, der durch die radialen Löcher des Kolbens (27) hindurch mit der axialen Bohrung (28) des Kolbens, die stromabwärts in der axialen Durchgangsbohrung (21) des Körpers offen ist, in Verbindung steht, die das Kühlfluid bis zur radialen Fluidpassage (17) im Düsenkörper leitet.
  7. Düse zum Kühlen nach Anspruch 6, dadurch gekennzeichnet, daß der ringförmige Verschlußsitz (11) ein ringförmiger Paßring (30) ist, der in der axialen Durchgangsbohrung (21) des Düsenkörpers (1) befestigt ist.
  8. Motor mit innerer Verbrennung enthaltend mindestens eine Düse mit einem Kolben nach irgendeinem der Ansprüche 1 bis 7.
EP20020356115 2001-07-04 2002-06-21 Spritzdüse für Kolbenkühlung Revoked EP1273774B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0109046 2001-07-04
FR0109046A FR2827009B1 (fr) 2001-07-04 2001-07-04 Gicleur de refroidissement a piston

Publications (2)

Publication Number Publication Date
EP1273774A1 EP1273774A1 (de) 2003-01-08
EP1273774B1 true EP1273774B1 (de) 2006-09-13

Family

ID=8865247

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20020356115 Revoked EP1273774B1 (de) 2001-07-04 2002-06-21 Spritzdüse für Kolbenkühlung

Country Status (9)

Country Link
US (1) US6672262B2 (de)
EP (1) EP1273774B1 (de)
CN (1) CN100404812C (de)
AT (1) ATE339605T1 (de)
BR (1) BR0202521B1 (de)
DE (1) DE60214626T2 (de)
ES (1) ES2271205T3 (de)
FR (1) FR2827009B1 (de)
PT (1) PT1273774E (de)

Families Citing this family (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10214830A1 (de) * 2002-04-04 2004-01-08 Mahle Gmbh Öleinlass für einen mit Kühlkanal versehenen Kolben eines Verbrennungsmotors
FR2844002B1 (fr) * 2002-09-02 2006-03-31 Bontaz Centre Sa Gicleur a projections multiples pour refroidissement de moteur, et moteurs equipes de tels gicleurs
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
DE10261180A1 (de) * 2002-12-20 2004-07-01 Daimlerchrysler Ag Temperaturgeregelte Ölspritzdüse zur Kolbenkühlung
US7152623B2 (en) * 2003-09-09 2006-12-26 Metaldyne Company, Llc Fluid jet for providing fluid under pressure to a desired location
US7086354B2 (en) 2003-10-29 2006-08-08 Deere & Company Cooling nozzle mounting arrangement
US7063049B2 (en) * 2004-03-03 2006-06-20 Deere & Company Directed spray jet and installation tool
US20060169331A1 (en) * 2004-08-09 2006-08-03 Neto Jose C Fluid jet with noise reducing sleeve
WO2006069075A2 (en) * 2004-12-21 2006-06-29 Metaldyne Fluid jet with noise reducing sleeve
FR2885170B1 (fr) 2005-05-02 2007-09-21 Bontaz Ct Sa Clapet a fuite controlee pour gicleur de refroidissement de piston
FR2913723B1 (fr) 2007-03-16 2009-06-12 Bontaz Ct Soc Par Actions Simp Gicleur de refroidissement a clapet
US8397749B2 (en) * 2007-09-07 2013-03-19 Metaldyne Company Llc Piston cooling jet with tracking ball orifice
EP2282089B1 (de) 2009-08-05 2019-02-20 HAWE Hydraulik SE Hydraulikventil
CN101865015B (zh) * 2010-06-02 2011-11-16 奇瑞汽车股份有限公司 一种活塞冷却喷嘴
JP5827164B2 (ja) * 2012-04-04 2015-12-02 トヨタ自動車株式会社 オイルジェット
US8875668B2 (en) * 2012-08-31 2014-11-04 Honda Motor Co., Ltd. Apparatus configured to shelter oil-jet device from inadvertent installation damage
JP5680601B2 (ja) * 2012-09-29 2015-03-04 大豊工業株式会社 ピストンクーリングジェット
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
JP6030585B2 (ja) 2014-01-17 2016-11-24 トヨタ自動車株式会社 オイルジェットバルブの取付方法
GB201519640D0 (en) * 2015-11-06 2015-12-23 Gm Global Tech Operations Inc Piston cooling jet for an internal combustion engine
CN105736112B (zh) * 2016-02-05 2018-04-24 重庆科克发动机技术有限公司 一种发动机冷却润滑油喷嘴
DE102016202643A1 (de) * 2016-02-22 2017-08-24 Mahle International Gmbh Kolben einer Brennkraftmaschine
CN106762079A (zh) * 2016-12-09 2017-05-31 重庆小康工业集团股份有限公司 发动机活塞冷却机构
CN106499493B (zh) * 2016-12-09 2020-03-10 重庆小康工业集团股份有限公司 发动机活塞冷却用喷油头
FR3067437B1 (fr) * 2017-06-13 2019-08-02 Bontaz Centre R & D Gicleur de fluide axial a clapet evente
US10704450B2 (en) * 2017-06-16 2020-07-07 Illinois Tool Works Inc. Piston cooling jet assembly
CN110730859B (zh) * 2017-07-07 2022-12-30 沃尔沃卡车集团 用于冷却发动机活塞的喷嘴
DE102017223465A1 (de) 2017-12-20 2019-06-27 Volkswagen Aktiengesellschaft Kolbenkühldüse
US11333140B2 (en) * 2019-06-11 2022-05-17 Caterpillar Inc. Cooling block for multi-cylinder air compressor
USD928201S1 (en) * 2019-08-02 2021-08-17 Transportation Ip Holdings, Llc Piston cooling apparatus
USD921044S1 (en) * 2019-08-02 2021-06-01 Transportation Ip Holdings, Llc Piston cooling apparatus
CN110682213A (zh) * 2019-11-13 2020-01-14 浙江方圆机床制造有限公司 砂轮修整器
FR3103244B1 (fr) * 2019-11-15 2022-12-23 Bontaz Centre R&D Clapet à piston compact
WO2021224903A1 (en) * 2020-05-03 2021-11-11 Yaacobi Amnon Method and system for controlling the temperature of an engine
DE102021115936A1 (de) * 2020-07-08 2022-01-13 Transportation Ip Holdings, Llc Kolbenkühldüse
USD965029S1 (en) * 2020-09-11 2022-09-27 Transportation Ip Holdings, Llc Piston cooling jet
DE102022105567A1 (de) 2022-03-09 2023-09-14 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Einspritzventil und Elektromaschine mit einem Einspritzventil

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2800119A (en) * 1955-05-05 1957-07-23 Maschf Augsburg Nuernberg Ag Arrangement for cooling the piston of internal combustion engines
DE2141518A1 (de) * 1971-08-19 1973-02-22 Kloeckner Humboldt Deutz Ag Hubkolbenbrennkraftmaschine mit innerer kuehlung der arbeitskolben durch schmieroel
DE4018363A1 (de) * 1990-06-08 1991-12-12 Wahler Gmbh & Co Gustav Drucksteuerventil, insbesondere fuer oelspritzduesen fuer brennkraftmaschinen
FR2719868B1 (fr) * 1994-05-10 1996-06-21 Bontaz Centre Gicleur de refroidissement de piston pour moteur à combustion interne.
JP3106058B2 (ja) * 1994-05-20 2000-11-06 株式会社ユニシアジェックス 内燃機関における潤滑・冷却装置
CN2272493Y (zh) * 1996-05-22 1998-01-14 杭州汽车发动机厂 四缸柴油机用活塞冷却装置
EP0947285A1 (de) * 1998-03-31 1999-10-06 Senior Engineering Investments AG Vorrichtung mit Spritzrohr für Fahrzeugmotor und Verfahren zu ihrer Herstellung

Also Published As

Publication number Publication date
EP1273774A1 (de) 2003-01-08
BR0202521A (pt) 2003-05-13
FR2827009B1 (fr) 2003-12-12
BR0202521B1 (pt) 2011-03-09
US20030005893A1 (en) 2003-01-09
DE60214626T2 (de) 2007-10-04
FR2827009A1 (fr) 2003-01-10
US6672262B2 (en) 2004-01-06
DE60214626D1 (de) 2006-10-26
ATE339605T1 (de) 2006-10-15
ES2271205T3 (es) 2007-04-16
CN100404812C (zh) 2008-07-23
PT1273774E (pt) 2007-01-31
CN1395031A (zh) 2003-02-05

Similar Documents

Publication Publication Date Title
EP1273774B1 (de) Spritzdüse für Kolbenkühlung
EP1980729B1 (de) Kühlungseinspritzdüse mit einer Klappe
CA2544956A1 (fr) Clapet a fuite controlee pour gicleur de refroidissement de piston
CA2864629C (fr) Injecteur de carburant pour une turbomachine
EP2006587B1 (de) Dichtungsventilsystem
FR3067437B1 (fr) Gicleur de fluide axial a clapet evente
FR3045735A1 (fr) Pompe de pressurisation de fluide et systeme de pressurisation de fluide
FR2800691A1 (fr) Amortisseur de direction pour une direction assistee hydraulique
FR2519074A1 (fr) Regleur hydraulique pour culbuterie de moteur a combustion interne
CA1233051A (fr) Frein de recul hydropneumatique a recuperation d'energie pour pieces d'artillerie et armes a feu
EP0682175A1 (de) Spritzdüse für Kolbenkühlung für eine Brennkraftmaschine
EP1937983B1 (de) Ventil mit gedämpftem öffnungssystem
EP0269471B1 (de) Hydraulische Drehdurchführung mit Stabilisierung der Temperatur
EP2104780A1 (de) Verbrennungsmotor für ein kraftfahrzeug mit einem wasserpumpen entgasungskanal
BE1010235A3 (fr) Buse d'injection de carburant.
FR2973077A1 (fr) Regulateur de pression comportant un moteur
EP1229245B1 (de) Austauschvorrichtung für einen geschlossenen Kreislauf
EP1183467B1 (de) Hochdruckpumpe mit verbesserter dichtung
EP0785344B1 (de) Aufsteckbare Kühlungsöldüse
EP1171724B1 (de) Asymmetrischer dämpfer für eine radaufhängung eines kraftfahrzeugs
FR2655702A1 (fr) Dispositif formant vanne de regulation pour circuit de lubrification d'un moteur thermique.
FR2976621A1 (fr) Systeme d'alimentation d'un gicleur d'huile pour un moteur a combustion
EP1004843A1 (de) Vorrichtung zu einer temperaturabhängigen Steuerung der Vorlaufgeschwindigkeit eines Geschützes
EP1183466B1 (de) Hochdruckpumpe
FR2720468A1 (fr) Clapet à bille avec butée.

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20030704

AKX Designation fees paid

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20060913

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060913

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060913

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: FRENCH

REF Corresponds to:

Ref document number: 60214626

Country of ref document: DE

Date of ref document: 20061026

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20061108

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061213

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061213

REG Reference to a national code

Ref country code: PT

Ref legal event code: SC4A

Free format text: AVAILABILITY OF NATIONAL TRANSLATION

Effective date: 20061124

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2271205

Country of ref document: ES

Kind code of ref document: T3

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PLAX Notice of opposition and request to file observation + time limit sent

Free format text: ORIGINAL CODE: EPIDOSNOBS2

26 Opposition filed

Opponent name: BING POWER SYSTEMS GMBH

Effective date: 20070612

PLBB Reply of patent proprietor to notice(s) of opposition received

Free format text: ORIGINAL CODE: EPIDOSNOBS3

BERE Be: lapsed

Owner name: BONTAZ CENTRE

Effective date: 20070630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070630

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070630

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061214

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070630

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20080530

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20080527

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: TR

Payment date: 20080617

Year of fee payment: 7

Ref country code: PT

Payment date: 20080528

Year of fee payment: 7

Ref country code: IT

Payment date: 20080626

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20080627

Year of fee payment: 7

Ref country code: IE

Payment date: 20080526

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20080618

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20080630

Year of fee payment: 7

RDAF Communication despatched that patent is revoked

Free format text: ORIGINAL CODE: EPIDOSNREV1

RDAG Patent revoked

Free format text: ORIGINAL CODE: 0009271

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: PATENT REVOKED

27W Patent revoked

Effective date: 20090113

GBPR Gb: patent revoked under art. 102 of the ep convention designating the uk as contracting state

Effective date: 20090113

REG Reference to a national code

Ref country code: PT

Ref legal event code: MP4A

Effective date: 20090617

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070621

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060913