EP3494291A1 - Poussoir hydraulique - Google Patents

Poussoir hydraulique

Info

Publication number
EP3494291A1
EP3494291A1 EP17748575.2A EP17748575A EP3494291A1 EP 3494291 A1 EP3494291 A1 EP 3494291A1 EP 17748575 A EP17748575 A EP 17748575A EP 3494291 A1 EP3494291 A1 EP 3494291A1
Authority
EP
European Patent Office
Prior art keywords
cavity
plunger
valve unit
hydraulic tappet
main body
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
EP17748575.2A
Other languages
German (de)
English (en)
Other versions
EP3494291B1 (fr
Inventor
Thomas Carl Edelmayer
Stefano FARISE'
Umberto Fasanotto
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.)
GNUTTI CARLO SpA
Original Assignee
GNUTTI CARLO SpA
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 GNUTTI CARLO SpA filed Critical GNUTTI CARLO SpA
Publication of EP3494291A1 publication Critical patent/EP3494291A1/fr
Application granted granted Critical
Publication of EP3494291B1 publication Critical patent/EP3494291B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2411—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the valve stem and rocker arm
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2305/00—Valve arrangements comprising rollers

Definitions

  • This invention relates to a hydraulic tappet.
  • hydraulic tappet normally means a tappet equipped with a hydraulic telescopic device, connected to the lubricating circuit of the motor, which, with its travel, is able to automatically recover the clearance existing between the tappet and the valves actuated by it.
  • the above-mentioned clearance is to be considered the result of multiple components such as, for example, machining tolerances, thermal expansion and wear of parts after their normal use.
  • this invention relates to a hydraulic tappet for internal combustion engines comprising a rocker arm supporting a plunger designed to actuate a valve.
  • It is basically plungers integrated in telescopic hydraulic means.
  • hydraulic telescopic elements of known type are in the form of an assembled cartridge which comprises an outer jacket and an inner plunger engaged slidably with each other.
  • valve unit integral n movement with the plunger.
  • the aim of this invention is provide a hydraulic tappet which is able to overcome the drawbacks of the prior art and which is at same time inexpensive to make, practical to operate and simple to install.
  • FIG. 1 is a schematic top plan view of a preferred embodiment of the hydraulic tappet made according to this invention.
  • FIG. 2 is a cross-sectional view of the hydraulic tappet of Figure 1 , according to the plane through the line ll-ll of Figure 1 ;
  • FIG. 2a is an enlarged view, with some parts cut away in order to better illustrate others, of a detail of Figure 2;
  • FIGS. 5 and 6 are respective cross-sectional views, with some parts cut away, of a variant embodiment of the tappet of the preceding drawings, in two different operating configurations.
  • the reference numeral 1 denotes in its entirety a hydraulic tappet for an internal combustion engine (not illustrated), made in accordance with this invention.
  • the hydraulic tappet 1 comprises a rocker 2 and a device 3 for recovering the clearance between the tappet and one or more valves, not illustrated, actuated by it.
  • the rocker 2 has a central hole 4 designed to house a shaft, not illustrated, for oscillation of the rocker 2 about a respective axis A1 of oscillation.
  • the rocker 2 has a first arm B1 and a second arm B2 positioned, respectively, on opposite sides relative to the central hole 4.
  • the first arm B1 is designed to support a follower element, not illustrated, configured for engaging, in known manner, with a cam, which is also not illustrated, in a cam-follower mechanism.
  • the second arm B2 has, at a distal end relative to the central hole 4, a through cavity 5 extending with axial symmetry.
  • the through cavity 5 extending with axial symmetry has a central axis A2 skew relative to the above-mentioned axis A1 of oscillation of the rocker.
  • the through cavity 5 has an inner wall 5a, a lower outlet 6 and an upper outlet 7, the latter being longitudinally opposite each other.
  • the lower outlet 6 of the cavity 5 advantageously has a smaller diameter than that of the upper mouth 7.
  • the inner wall 5a has a threaded portion F.
  • the device 3 for recovering the clearance between the tappet and one or more valves, not illustrated, actuated by it.
  • the device 3 for recovering the clearance comprises a plunger 8 slidably engaged inside the above-mentioned cavity 5 and emerging from it partially at the relative lower outlet 6.
  • the portion of the plunger 8 emerging from the lower outlet 6 of the cavity 5 supports an articulated member 9 for pushing the one or more valves, not illustrated, of the internal combustion engine.
  • the above-mentioned pushing element 9 is advantageously configured, in known manner, in a bell-bottom fashion, and connected to the plunger 8 by means of an articulated ball joint S.
  • the device 3 for recovering the clearance comprises, in the proximity of the above-mentioned upper mouth 7 of the cavity 5, a check valve unit 10 for adjusting a flow of oil circulating inside the above-mentioned cavity 5, a plunger 8 and a first helical spring M1 interposed between the above- mentioned valve unit 10 and the plunger 8.
  • the valve unit 10 comprises a main body 1 1 having cylindrical dimensions which is located inside the cavity 5 closing the upper mouth 7.
  • the main body 1 1 has an outer threaded wall 1 1 a and is designed to engage by screwing with the above-mentioned threaded portion F of the wall 5a inside the cavity 5.
  • the main body 1 1 is fixed inside the cavity 5 by friction connection through forced insertion (also known as pressing).
  • the main body 1 1 protrudes above the cavity 5 so as to allow the screwing of a ring nut 13 for clamping on the relative outer threaded wall 1 1 a.
  • the ring nut 13 is defined by a locknut.
  • the ring nut has an external thread designed to engage by screwing with the threaded portion F of the wall 5a of the cylindrical cavity 5.
  • the tank 14 is advantageously cylindrical in shape.
  • the tank 14 is covered by a specific cover 15 applied at the top, towards the outside.
  • the cover 15 has the shape of a dome.
  • a housing 16 is made on the main body 1 1 for a ball 17 for retaining the oil.
  • the ball 17 is retained inside the housing 16 by a containment cage 16a of substantially known type.
  • the valve unit 10 comprises a second helical spring M2 positioned at least partly inside the housing 16 and designed to apply a relative elastic action against the ball 17, for pushing the latter away from the tank.
  • the plunger 8 has a lower portion 8a (with reference to the relative configuration with respect to the rocker 2) with an approximately hemispherical shape, to engage with the above-mentioned articulated pushing element 9 of the one or more or valves, not illustrated, of the internal combustion engine.
  • the plunger 8 has an upper end portion 8b with diametric dimensions greater than the lower portion 8a.
  • the plunger 8 also has an intermediate portion 8c interposed between the above-mentioned upper 8a and lower 8b portions.
  • the intermediate 8c portion slidably engages with the lower outlet 6 of the cavity 5.
  • the intermediate portion 8c has diametric dimensions less than the upper portion 8b.
  • the plunger 8 supports an annular sealing element 18 mounted on it externally and designed to guarantee the dynamic seal between the plunger 8 and the inside wall 5a of the cavity 5 during the sliding of the plunger 8 along the axis A2.
  • the plunger 8 is positioned with the elative upper portion 8b facing the main body 1 1 of the valve unit 10.
  • the plunger 8 at the relative above-mentioned upper portion 8b, has inside it a cavity 19 for housing and guiding the above-mentioned first helical spring M1 , the housing cavity 19 being shaped in the form of a cylindrical crown.
  • housing cavity 19 in the shape of a cylindrical crown, is delimited, in the respective internal diameter, by a cylindrical pin 20 coaxial with the plunger 8.
  • the cylindrical pin 20 is returned inside a hole 21 made in the plunger 8.
  • the cylindrical pin 20 is made of plastic material.
  • the plunger 8 and the main body 1 1 of the valve unit are mechanically separate, and physically separated along the direction of the axis A2.
  • a high pressure chamber 22 between the plunger 8 and the main body 1 1 is defined a high pressure chamber 22, the chamber 22 having a variable volume as a function of the sliding of the plunger 8.
  • the chamber 22 is defined by high pressure since the oil in it reaches maximum pressure values due to the compression action to which it is subjected in use.
  • the above-mentioned high pressure chamber 22 has the shape of a disc.
  • the disc-shaped chamber 22 has diameter substantially equal to that of the plunger 8 at its above- mentioned upper end portion 8b facing the valve unit 10.
  • the variability of the volume of the high pressure chamber 22, consequent to the sliding of the plunger along the cavity 5 according to the direction of the axis A2, advantageously allows, in a substantially known manner, the recovery of any clearance existing between the tappet 1 and the valves, not illustrated, of the internal combustion engine.
  • connecting conduit 23 configured to place them in fluid communication with each other.
  • the above-mentioned ball 17 is located along the above-mentioned connecting conduit 23 and is designed to obstruct it, under certain operating conditions, that is to say, when the pressure of the oil in the chamber 22 becomes such as to exceed the opposing elastic action exerted on the ball 17 by the second helical spring M2.
  • the ball 17 is designed to close the connecting conduit 23 when the pressure in the high pressure chamber 22 is greater than that existing in the tank 14, the second spring helical M2 performing basically the function of preventing unwanted blockages of the ball 17 in its cavity
  • the spring M2 is designed to keep the ball 17 in a position such as not to obstruct the channel 23 when the pressure in the tank 14 is greater than or equal to the pressure in the high pressure cavity 22.
  • the check valve unit 10 is of the type normally open.
  • the spring M2 is configured in such a way as to delay the closing of the check valve unit 10, to allow the plunger 8 to move along the cavity 5 to compensate for any wear and thermal expansion.
  • the tank 14 is formed integrated in the valve unit 10.
  • This feature allows a modular and rapid assembly of the hydraulic tappet 1 .
  • the tank 14 is formed integrated in the main body 1 1 of the valve unit 10.
  • Figures 5 and 6 illustrate, relative to the second embodiment of the tappet 1 equipped with clamping ring nut 13, two different positions adopted by the main body 1 1 of the valve unit 10.
  • Figure 5 shows a condition of maximum screwing of the body 1 1 whilst Figure 6 shows a condition of only partial screwing of the body 1 1 .
  • the position of the main body 1 1 inside the cavity 5 can be adjusted through different degrees of screwing.
  • minimising its volume means guaranteeing greater rigidity to the system in its entirety, taking into account the inevitable presence of air in the oil contained inside it (at least in certain operating phases of the motor) and the consequent compressibility.
  • a first advantage provided by the tappet 1 according to this invention is due to the fact that the plunger 8 is slidable directly on the through cavity 5 made on the rocker, without requiring the presence of any containment jacket as in prior art solutions.
  • Another advantage resulting from this invention is due to the limitation of the number of components of the tappet: sliding the plunger 8 directly on the inner wall 5a of the cavity 5 means that no additional jacket is in fact required.
  • a direct consequence of this circumstance is less stress on the components, such as, for example, the valve unit 10 or the annular sealing unit 18 which will also be subjected to less wear.
  • the main body 1 1 of the valve unit is stationary relative to the rocker 2 which it supports, thus guaranteeing a greater overall rigidity of the system.
  • a further advantage results from the construction of the intermediate portion 8c of the plunger 8 with diametric dimensions less than the upper portion 8b.
  • This configuration allows, in effect, a smaller overall size of the rocker 2 at the lower outlet 6 whilst guaranteeing a considerable diametric size of the high pressure chamber 22. In this way, that is to say, with a large chamber 22, it is possible, with the same force acting on the plunger 8, to lower the pressure value reached inside it, thereby limiting the general mechanical stress of the system.
  • Yet another advantage is due to the possibility of assembling the same in a modular fashion: inside the cavity 5 there are in fact basically inserted only two components, that is to say, the valve unit 10 and the plunger 8.
  • the ease of assembly of the tappet according to the invention is also due to the fact that the valve unit 10 is physically separate from the plunger 8.
  • the valve unit 10 is pre-assembled and advantageously its operation may also be tested before being mounted inside a specific tappet.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Lubricants (AREA)

Abstract

L'invention concerne un poussoir hydraulique d'un moteur à combustion interne, comprenant un culbuteur (2) oscillant autour d'un axe respectif (A1 ) d'oscillation pour commander le déplacement d'au moins une soupape. Le culbuteur (2) comporte au niveau d'un bras relatif (B2) une cavité traversante (5) s'étendant avec une symétrie axiale ayant un axe central (A2) en biais par rapport à l'axe d'oscillation (A1) déjà mentionné. La cavité (5) comporte une paroi interne (5a), une sortie inférieure (6) et une sortie supérieure (7) longitudinalement opposé l'une de l'autre. Un piston (8) s'engage de manière coulissante à l'intérieur de la cavité (5) et sort de celle-ci partiellement au niveau de la sortie inférieure relative (6), le piston (8) étant configuré pour coopérer avec un élément respectif (9) pour pousser au moins une soupape. Une unité de clapet de non-retour (10) est conçue pour ajuster un flux d'huile circulant à l'intérieur de la cavité (5), et comprend un corps principal situé à l'intérieur de la cavité (5) pour fermer la sortie supérieure relative (7).
EP17748575.2A 2016-08-05 2017-07-31 Poussoir de soupape hydraulique Active EP3494291B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT102016000083173A IT201600083173A1 (it) 2016-08-05 2016-08-05 Punteria idraulica.
PCT/IB2017/054642 WO2018025149A1 (fr) 2016-08-05 2017-07-31 Poussoir hydraulique

Publications (2)

Publication Number Publication Date
EP3494291A1 true EP3494291A1 (fr) 2019-06-12
EP3494291B1 EP3494291B1 (fr) 2021-02-17

Family

ID=58159290

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17748575.2A Active EP3494291B1 (fr) 2016-08-05 2017-07-31 Poussoir de soupape hydraulique

Country Status (4)

Country Link
EP (1) EP3494291B1 (fr)
CN (1) CN109790764B (fr)
IT (1) IT201600083173A1 (fr)
WO (1) WO2018025149A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3322882B1 (fr) * 2015-07-16 2023-01-11 Eaton Intelligent Power Limited Système de distribution à soupapes
US11242774B2 (en) 2019-09-20 2022-02-08 Caterpillar Inc. Rocker assembly with a hydraulic lash adjuster

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR752332A (fr) * 1932-04-04 1933-09-20 Perfectionnements au mécanisme de commande des soupapes des moteurs à combustion interne
DE1123865B (de) * 1957-07-12 1962-02-15 Renault Ventilspielausgleichsvorrichtung an Brennkraftmaschinen
GB909707A (en) * 1958-02-05 1962-10-31 Renault Improvements in or relating to hydraulic devices for taking up axial play in valve gears, notably of internal combustion engines
DE4422080A1 (de) * 1994-06-24 1995-09-21 Audi Ag Schwinghebel zur Betätigung eines Ventils einer Brennkraftmaschine
US5758613A (en) * 1997-01-30 1998-06-02 Eaton Corporation Hydraulic lash adjuster and biased normally open check valve system therefor
WO2005113942A1 (fr) * 2004-05-13 2005-12-01 Schaeffler Kg Dispositif de rattrapage de jeu hydraulique
JP2011157843A (ja) * 2010-01-29 2011-08-18 Isuzu Motors Ltd エンジンの弁作動特性変更装置に用いられる電磁弁
JP5567856B2 (ja) * 2010-02-24 2014-08-06 トヨタ自動車株式会社 密閉型ラッシュアジャスタ
CN202140128U (zh) * 2011-02-25 2012-02-08 奚勇 集成式的泄气型发动机制动装置
CN103696822B (zh) * 2013-12-23 2016-04-06 宁波华液机器制造有限公司 一种带液压挺柱的驱动器

Also Published As

Publication number Publication date
IT201600083173A1 (it) 2018-02-05
CN109790764B (zh) 2021-04-30
CN109790764A (zh) 2019-05-21
EP3494291B1 (fr) 2021-02-17
WO2018025149A1 (fr) 2018-02-08

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