EP2660459B1 - Réduction de charge - Google Patents

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Publication number
EP2660459B1
EP2660459B1 EP12166665.5A EP12166665A EP2660459B1 EP 2660459 B1 EP2660459 B1 EP 2660459B1 EP 12166665 A EP12166665 A EP 12166665A EP 2660459 B1 EP2660459 B1 EP 2660459B1
Authority
EP
European Patent Office
Prior art keywords
plunger
pump
region
tappet
spring seat
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.)
Not-in-force
Application number
EP12166665.5A
Other languages
German (de)
English (en)
Other versions
EP2660459A1 (fr
Inventor
Christopher Mccrindle
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.)
Delphi International Operations Luxembourg SARL
Original Assignee
Delphi International Operations Luxembourg SARL
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 Delphi International Operations Luxembourg SARL filed Critical Delphi International Operations Luxembourg SARL
Priority to EP12166665.5A priority Critical patent/EP2660459B1/fr
Priority to KR1020147033558A priority patent/KR101629903B1/ko
Priority to PCT/EP2013/058358 priority patent/WO2013164220A1/fr
Priority to US14/396,177 priority patent/US20150118066A1/en
Priority to CN201380023234.1A priority patent/CN104508292B/zh
Priority to JP2015509369A priority patent/JP6185985B2/ja
Publication of EP2660459A1 publication Critical patent/EP2660459A1/fr
Application granted granted Critical
Publication of EP2660459B1 publication Critical patent/EP2660459B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0435—Arrangements for disconnecting the pistons from the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0439—Supporting or guiding means for the pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/06—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means including spring- or weight-loaded lost-motion devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/02—Fuel-injection apparatus having means for reducing wear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped

Definitions

  • the present invention relates to a method and apparatus for selectively providing a fluid communication path that allows lubricant to flow to a desired location in between two moving parts.
  • the present invention relates to a plunger and tappet arrangement.
  • a resilient spring seat is used to separate the plunger and tappet by a short distance at a particular point of a cycle of the plunger movement. The momentary separation allows lubricant to flow from a surrounding region into the space created between the plunger and tappet.
  • an intermediate element often referred to as an intermediate drive member, and often in the form of a tappet, transmits drive from a cam mechanism to a pumping plunger.
  • the pumping plunger is used to pressurise fluid in a pumping chamber for delivery to a desired location.
  • the fluid could be engine fuel of a diesel engine fuel injection system.
  • Tappets are used to reduce lateral forces applied to a pumping plunger so that in general the pumping plunger is driven in a reciprocal motion by the tappet backwards and forwards along a respective longitudinal axis of motion.
  • Tappets are well known and are generally cup-shaped elements with a cylindrical side wall and solid base. Vents can be provided in the side wall and/or base of the tappet so that a lubricating fluid can flow from around the cam mechanism to regions within the tappet. This helps ensure hydraulic forces do not inhibit free movement of the tappet within a tappet bore in a housing.
  • pumps which can operate at high pressures, employ a reciprocating plunger to do work on the fluid being pumped.
  • the plunger is moved forward during a pumping stroke by applying a load mechanically to an opposite end of the plunger via a tappet.
  • a return spring On a return stroke of the cycle of motion of the plunger, the plunger is held against the tappet by a spring referred to as a return spring.
  • a pump assembly as defined in claim 1.
  • the spring seat member and said plunger element are integrally formed or the spring seat member is secured to said plunger element for movement therewith.
  • a method of lubricating between a plunger element of a pump assembly and an intermediate element providing drive to the plunger element comprising the steps as defined in claim 8.
  • the method further comprises cooling and removing debris from between the abutment surface and said contact region via the lubricating fluid.
  • the method further comprises providing a squeeze film layer between the abutment surface and said contact region via the lubricating fluid.
  • the method further comprises opening and closing a gap between said abutment surface and said contact region each cycle of the plunger element.
  • the portion of a cycle comprises an end of a return cycle of the plunger element in which the fluid in the pump bore expands and said first reciprocating motion further comprises a pump cycle portion in which fluid in the pump bore is compressed.
  • the method further comprises biasing the further end region via a spring seat member integrally formed with said plunger element or via a spring seat member secured to said plunger element for movement therewith.
  • Certain embodiments of the present invention provide the advantage that a fluid communication path between an end of a plunger and contact region of an intermediate element such as a tappet is provided. This allows lubricant to be drawn into the region between opposed faces and to cool, lubricate and wash away debris. This also provides a squeeze film between the opposed faces as they close back together so that the faces are kept apart for a longer period than would otherwise be allowed with prior known systems. This longer period reduces the wear created by drive motion and/or the inevitable lateral motion induced as part of the reciprocating pumping motion.
  • Certain embodiments of the present invention provide a method for reducing fretting and wear and for removing debris in a high pressure head of a pump assembly.
  • FIG. 1 illustrates- a pump assembly 100.
  • the pump assembly includes a main pump housing 101 provided with an axially extending opening 102. The opening extends in the direction into the page shown in Figure 1 .
  • a cam shaft (not shown) having an axis of rotation 103 drives an eccentrically mounted cam 104 mounted in the opening.
  • the main pump housing 101 is provided with a first, second and third radially extending opening or through bore 105a, 105b, 105c, each of which communicates at a radially inner end thereof with the axially extending opening 102 which extends through the housing.
  • Other numbers of through bores can of course be utilised according to certain other embodiments of the present invention.
  • a radially outer end of each housing bore 105a, 105b, 105c receives a respective pump head 110a, 110b, 110c.
  • Each pump head is substantially identical and therefore reference will be made hereinafter only to the upper pump head 110a shown in Figure 1 which is described and shown in the further drawings.
  • FIG. 2 illustrates parts of the pump head 110a in more detail.
  • the pump head includes a head portion 200 which is a substantially rectangular body.
  • a substantially cylindrical central region extends downwardly from an underside region 201 of the pump head.
  • the cylindrical extension 202 encompasses a substantially cylindrical pump bore region 203.
  • the pump bore 203 has a blind end 204 where at least one valve 205 is located.
  • the pump bore 203 also has an open end 206 which thus provides an open mouth of the extension of the pump head.
  • the bore 203 provides a pumping chamber with the space of the pumping chamber being defined by the blind end 204 of the bore and a first end 210 of a plunger 211.
  • the plunger is an elongate shaft-like member which slides backwards and forwards within the cylindrical bore 203 in the pump head. As an upper end surface 212 of the first end 210 of the plunger moves upwardly in the direction shown by arrow A in Figure 2 the volume of the pumping chamber reduces. Equally, as the plunger moves in the direction along the axis of movement opposite to the direction shown by arrow A in Figure 2 , the volume of the pumping chamber increases.
  • a substantially circular cut out region 215 is provided centrally on the lower surface of the pump head. This is utilised to locate and secure a first end 220 of a return spring 221.
  • the return spring holds the tappet away from the pump head in its relaxed state and is compressed as the tappet is urged towards the pump head during a pump stroke part of a cycle.
  • the space 215 under the pump head also provides clearance for an upper circular surface 230 of a cup-like tappet 231.
  • the blind end of the plunger bore thus defines together with an outer end face of the plunger a pump chamber into which fuel at relatively low pressure may be delivered and within which pressurisation of fuel to a relatively high level suitable for injection takes place as the plunger is driven to perform a pumping stroke upon rotation of the cam or a rider located on the cam.
  • the tappet 231 is a substantially hollow body having a cylindrical side wall 232 which extends from the circumferential region of a substantially circular base 233.
  • the base and side wall are integrally formed.
  • the lip of the side wall 232 forms the circular surface which is urged upwards towards the pump head during pumping.
  • the base 233 provides a blind end of an internal chamber 240 defined within the tappet.
  • One or more through holes 250 are formed circumferentially around the side wall of the tappet to enable fluid to flow from an outer region surrounding the tappet body to an inner region within the chamber 240.
  • the through holes may be circular or church window style or the like.
  • a spring seat 260 is located at a further end 261 of the plunger 211.
  • the spring seat 260 shown in Figure 2 is secured to the end of the plunger by an interference fit, although it will be appreciated that the spring seat could alternatively be integrally formed with the shaft-like plunger body or could be secured thereto via other ways.
  • the spring seat and plunger move together as one unit.
  • An upper surface 262 of the spring seat seats a further lower end 263 of the return spring.
  • the drive shaft co-operates with the cam 104 and as shown in Figure 1 an optional and co-operable generally tubular cam rider which extends coaxially with the cam.
  • the cam rider On the outer surface the cam rider is provided with a first, second and third flattened surface referred to as flats.
  • Each one of the flats co-operates with the base surface of a tappet 231 for a respective one of the plungers.
  • a tappet is operably coupled to a plunger, rotation of the shaft causes the cam rider to ride over the surface of the cam thereby imparting drive to both the tappet and the plunger.
  • a slipper face may be provided for promoting such sliding movement.
  • a lubricating fluid such as fuel or the like, is provided in the opening 102 of the housing and bore 105 in which the tappet slides to limit wear due to friction.
  • the tappet is caused to reciprocate in the opening 105 and the plunger is caused to reciprocate within the plunger bore 203. There is thus a first reciprocating motion of the tappet within the housing bore and a further reciprocating motion of the plunger within the pump bore.
  • the tappet and the pumping plunger are thus driven together causing the plunger to perform a pumping cycle including a pumping stroke during which the tappet and the plunger are driven radially outward from the central cam shaft (i.e. towards the respective pump head) which reduces the volume within the pump chamber 203.
  • the pumping plunger is driven inwardly within its plunger bore and fuel within the pump chamber is pressurised to a high level.
  • the tappet and plunger are urged in a radially inward direction, i.e. towards the centre of the housing and away from the pump head. This return motion is caused by virtue of the resilient nature of the return spring which thus biases the tappet away from the pump head.
  • the plunger is urged outwardly from the plunger bore and fuel at relatively low pressure may be allowed to fill the associated pump chamber via a valve.
  • the provision of the plunger return spring thus serves to urge the plunger to perform its return stroke and additionally ensures contact is maintained between the tappet and the flat of the cam rider during the pumping cycle.
  • the tappet and plunger perform cyclic sinusoidal motion and are driven at a desired frequency. Aptly, the maximum frequency is about around 130Hz. Aptly, the maximum frequency is about around 120Hz.
  • the tappet has a range of travel between bottom-dead-centre and top-dead-centre. Aptly, the range of travel is about around 15mm or less. Aptly, the range of travel is about around 10mm or less.
  • the tappet acts as an intermediate element between the cam and/or cam rider element which provides drive and the plunger which is driven in a reciprocal fashion within the pump bore provided by the pump head.
  • Figure 3 illustrates the pump head, tappet and return spring shown in Figure 2 in more detail.
  • Figure 3 helps clarify how church window style openings 250 are formed at a radially innermost end region of the tappet.
  • the openings are formed by cut out regions 300 from the cylindrical side wall and base of the tappet.
  • Figure 3 also helps illustrate how the pump head is substantially rectangular in shape, although it will be appreciated that other shapes and configurations are possible according to certain other embodiments of the present invention.
  • the pump head may be secured to the pump housing 101 via bolts or other such securing mechanisms which, in use, extend through the apertures 301 in the pump head.
  • the tappet thus provides an internal chamber which encompasses an end of the return spring.
  • the other end of the return spring is secured at an upper end thereof to the pump head 110.
  • Figure 4 illustrates how a plunger extends through the open end 206 of the pump bore into a chamber 240 defined within the tappet.
  • a lower end of the plunger 211 has a generally circular abutment surface end 400. This abuts with a central contact region 401 on an upper facing surface 402 of the base of the tappet. As illustrated in Figure 4 the central contact region 401 may be slightly raised with respect to a surrounding region of the upper surface 402 of the base of the tappet.
  • a spring seat 260 (see also Figure 2 ) is a substantially circular, ring-like body formed of a resilient material.
  • the spring seat is formed of hardened steel.
  • the cross-section of the spring seat is formed of a radially outermost (with respect to the axis of the plunger) leg 403 which has a lower annular contact surface 404 which sits on the upper surface 404 of the base of the tappet.
  • the contact point 405 between the spring seat and base of the tappet thus constrains motion of the spring seat in a direction shown by arrow B in Figure 4 .
  • the remaining body of the spring seat is generally disc-like with a concave profile on its underside.
  • the concave, partially teardrop shaped recess on the lower side of the spring seat helps allow the spring seat to flex.
  • the upper surface 262 (see also Figure 2 ) of the spring seat has an upper annular rib 410 extending as a ring shaped protuberance.
  • a small gap 420 can be opened between the end surface 400 of the plunger and the contact region 401 of the base of the tappet.
  • This space 420 provides a short separation between component parts.
  • the cam rider ceases to urge the tappet (and thus the plunger) in the direction opposite to arrow B.
  • the return spring 221 which acts on the upper surface of the spring seat which is urged against the base of the tappet and which carries the plunger with it, then causes motion of the tappet and plunger in the direction of arrow B.
  • the resilient nature of the spring seat and the fact that it stands on the base of the tappet causes the plunger end to momentarily be pulled away from the contact region 401 at the base of the tappet.
  • This separating motion creates the gap 420 that provides a fluid communication path between the zone between the component parts.
  • the fluid communication path also communicates with the chamber 240 within the tappet and, via the vents in the tappet 250, the surrounding regions.
  • Figure 5 helps illustrate the cylindrical nature of the tappet and circular disc-like nature of the spring seat in more detail.
  • the tappet 231 is a cup-like element having a cylindrical side wall extending from a substantially circular base.
  • An upper lip 230 of the cylindrical side wall of the tappet provides an open mouth to the tappet and the lip 230 may be urged upwardly towards the pump head into a recess 500 in the central circular inset region 215 on the underside of the pump head body 200.
  • Figure 5 also helps illustrate how a raised central region of the upper surface of the base of the tappet may be raised to provide an island 501 which includes a contact surface 401 of the tappet at its upper surface.
  • the upper surface 262 of the spring seat provides an outermost substantially flat ring surface 505 which then extends upwardly via an upwardly extending region 506 into the upwardly facing rib region 410. This helps locate/seat the end of the return spring. From the rib moving radially inwards towards the plunger, the upper surface of the spring seat then drops into a first concave region 510 separated from an inner concave region 511 by a convex region 512.
  • the radially innermost central region of the spring seat provides a contact region to enable the spring seat to be secured via an interference fit or the like to the end 261 of the plunger. It will be appreciated that the plunger body and spring seat could optionally be integrally formed.
  • a spring feature is thus added between a plunger and tappet or similar component.
  • This causes a small gap to be opened between the component parts when unloaded.
  • the opening of the small gap operates to draw lubricant into the gap between the faces.
  • This enables the faces to be cooled, lubricated and cleared of debris.
  • the flow of lubricant into the contact region also provides a squeeze film to be provided. This squeeze film helps keep the opposed faces apart for a longer period than would otherwise be possible with prior known systems. This helps reduce the wear created by motion.
  • the spring effect may be provided by a resilient spring seat as described hereinabove.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (13)

  1. Assemblage de pompe (100) comprenant :
    un boîtier de pompe (101) comprenant une ouverture s'étendant axialement (102) et au moins un perçage de boîtier s'étendant généralement radialement depuis ladite ouverture (102) ;
    au moins un élément intermédiaire (231) reçu chacun pour un mouvement de coulissement en va-et-vient dans un perçage de boîtier respectif et comprenant une région de chambre intense ;
    au moins une tête de pompe (110a) comprenant un perçage de pompe (105a) ayant une extrémité borgne et fixée sur ledit boîtier de pompe (101) ;
    un élément plongeur allongé (211) dans chaque région de chambre et susceptible d'être entraîné en utilisation via un élément intermédiaire respectif (231), et comprenant une première région terminale qui pressurise le fluide dans une chambre de pompage prévue par un perçage de pompe respectif, et une autre région terminale ;
    une came et/ou un élément suiveur de came dans ladite ouverture s'étendant axialement (102) ayant une surface intérieure adaptée à coopérer avec un arbre d'entraînement de came et une surface extérieure capable de coopérer avec une surface d'entraînement dudit élément intermédiaire (231),
    caractérisé en ce que la pompe (100) comprend en outre au moins un élément formant siège (260) pour ressort élastique, généralement semblable à un disque avec un profil concave sur une face inférieure, capable de fléchir, et agencé à une autre région terminale (261) de l'élément plongeur (211) qui sollicite l'autre région terminale en éloignement d'une région de contact de l'élément intermédiaire (231) pendant une portion d'un cycle de mouvement de l'élément plongeur (211) pour assurer grâce à cela un trajet de communication fluidique entre une surface de butée (400) de l'autre région terminale et ladite région de contact (401).
  2. Assemblage de pompe selon la revendication 1, dans lequel l'élément intermédiaire comprend un opercule (231) reçu pour un mouvement de coulissement en va-et-vient dans le perçage de boîtier (105a).
  3. Assemblage de pompe selon la revendication 2, dans lequel l'opercule (231) comprend au moins un trou traversant (250) dans une paroi latérale cylindrique et/ou dans une paroi de base de lui-même, ledit trou traversant assurant une portion de trajet fluidique connectée audit trajet de communication fluidique (420).
  4. Assemblage de pompe selon l'une quelconque des revendications précédentes, dans lequel le trajet de communication fluidique (420) fournit un fluide de lubrification entre ladite surface de butée (400) et ladite région de contact (401) à la fin d'un cycle de retour de l'élément plongeur (211).
  5. Assemblage de pompe selon l'une quelconque des revendications précédentes, dans lequel la première région terminale (210) dudit élément plongeur est capable de se placer dans une extrémité borgne du perçage de pompe (105a), et l'élément intermédiaire (231) comprend en outre une surface d'entraînement qui peut être entraînée par la came ou par l'élément suiveur de came.
  6. Assemblage de pompe selon l'une quelconque des revendications précédentes, comprenant en outre un élément formant ressort de rappel qui force une surface de l'élément formant siège de ressort en éloignement d'une tête de pompe (110a) d'un assemblage de pompe (100).
  7. Assemblage de pompe selon l'une quelconque des revendications précédentes, dans lequel ledit élément formant siège de ressort (260) et ledit élément plongeur (211) sont intégralement formés, ou bien l'élément formant siège de ressort (260) est attaché audit élément plongeur (211) pour un déplacement avec celui-ci.
  8. Procédé de lubrification entre un élément plongeur (211) d'un assemblage de pompe (100) et un élément intermédiaire (231) assurant un entraînement de l'élément plongeur (211), le procédé comprenant les étapes consistant à :
    entraîner une première région d'extrémité (210) d'un élément plongeur (211) dans un premier mouvement en va-et-vient par rapport à une extrémité borgne d'un perçage de pompe (105a) d'une tête de pompe (110a) en forçant sélectivement une région de contact d'un élément intermédiaire (231) à proximité d'une autre région d'extrémité (261) de l'élément plongeur (211) dans un autre mouvement en va-et-vient ;
    via un élément formant siège (260) pour ressort élastique, généralement semblable à un disque avec un profil concave sur une face inférieure, capable de fléchir et agencé au niveau de l'autre région terminale (261) de l'élément plongeur, solliciter l'autre région terminale en éloignement d'une région de contact de l'élément intermédiaire (231) pendant une portion d'un cycle de mouvement de l'élément plongeur (211), de telle façon qu'un trajet de communication fluidique est assuré entre une surface de butée (400) de ladite autre région terminale et ladite région de contact (401) lorsque l'autre région terminale est sollicitée en éloignement de l'élément intermédiaire (231).
  9. Procédé selon la revendication 9, comprenant en outre :
    les opérations consistant à refroidir et à supprimer des débris depuis entre la surface de butée (400) et ladite région de contact (401) via le fluide de lubrification.
  10. Procédé selon la revendication 8 ou 9, comprenant en outre :
    l'opération consistant à prévoir une couche de film de serrage entre la surface de butée (400) et ladite région de contact (401) via le fluide de lubrification.
  11. Procédé selon l'une quelconque des revendications 8 à 10, comprenant en outre :
    les opérations consistant à ouvrir et fermer un intervalle (420) entre ladite surface de butée (400) et ladite région de contact (401) à chaque cycle de l'élément plongeur (211).
  12. Procédé selon l'une quelconque des revendications 8 à 11, comprenant en outre :
    ladite portion d'un cycle comprend une fin d'un cycle de retour de l'élément plongeur dans laquelle le fluide dans le perçage de pompe se détend et ledit premier mouvement en va-et-vient comprend en outre une portion d'un cycle de pompe dans laquelle du fluide dans le perçage de pompe est comprimé.
  13. Procédé selon l'une quelconque des revendications 8 à 12, comprenant en outre :
    l'opération consistant à solliciter l'autre région terminale (261) via un élément formant siège de ressort (260) intégralement formé avec ledit élément plongeur (211), ou via un élément formant siège de ressort attaché audit élément plongeur pour un mouvement avec celui-ci.
EP12166665.5A 2012-05-03 2012-05-03 Réduction de charge Not-in-force EP2660459B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP12166665.5A EP2660459B1 (fr) 2012-05-03 2012-05-03 Réduction de charge
KR1020147033558A KR101629903B1 (ko) 2012-05-03 2013-04-23 부하 감소
PCT/EP2013/058358 WO2013164220A1 (fr) 2012-05-03 2013-04-23 Réduction de charge
US14/396,177 US20150118066A1 (en) 2012-05-03 2013-04-23 Load reduction
CN201380023234.1A CN104508292B (zh) 2012-05-03 2013-04-23 泵组件和润滑方法
JP2015509369A JP6185985B2 (ja) 2012-05-03 2013-04-23 荷重低減

Applications Claiming Priority (1)

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EP12166665.5A EP2660459B1 (fr) 2012-05-03 2012-05-03 Réduction de charge

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EP2660459A1 EP2660459A1 (fr) 2013-11-06
EP2660459B1 true EP2660459B1 (fr) 2016-04-06

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EP12166665.5A Not-in-force EP2660459B1 (fr) 2012-05-03 2012-05-03 Réduction de charge

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US (1) US20150118066A1 (fr)
EP (1) EP2660459B1 (fr)
JP (1) JP6185985B2 (fr)
KR (1) KR101629903B1 (fr)
CN (1) CN104508292B (fr)
WO (1) WO2013164220A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB201517504D0 (en) * 2015-10-05 2015-11-18 Delphi Internat Operations Luxembourg S À R L Pumping assembly
GB201517506D0 (en) * 2015-10-05 2015-11-18 Delphi Internat Operations Luxembourg S À R L Pumping assembly
CN107939628B (zh) * 2017-12-26 2023-07-18 浙江三浪润滑科技有限公司 一种多头径向柱塞泵及其使用方法

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5512027U (fr) * 1978-07-07 1980-01-25
JPS5867965U (ja) * 1981-10-30 1983-05-09 いすゞ自動車株式会社 燃料噴射ポンプの送油圧力制御装置
JP2722766B2 (ja) * 1990-04-12 1998-03-09 株式会社デンソー 燃料噴射ポンプ
JPH05180116A (ja) * 1991-12-25 1993-07-20 Nippondenso Co Ltd 燃料噴射ポンプ
JPH094542A (ja) * 1995-06-20 1997-01-07 Nippondenso Co Ltd 燃料供給装置
JPH09303161A (ja) * 1996-05-14 1997-11-25 Kubota Corp ディーゼルエンジンの燃料噴射装置
JPH1030525A (ja) * 1996-07-16 1998-02-03 Denso Corp 高圧サプライポンプ
IT239879Y1 (it) * 1996-12-23 2001-03-13 Elasis Sistema Ricerca Fiat Perfezionamenti ad una pompa a pistoni, in particolare ad una pompa apistoni radiali per il carburante di un motore a combustione interna.
FI108071B (fi) * 1998-07-03 2001-11-15 Waertsilae Tech Oy Ab Integroitu pumppu- ja nostinyksikkö polttoaineensyöttöjärjestelmässä
JP3867758B2 (ja) * 1999-06-22 2007-01-10 株式会社デンソー 高圧サプライポンプ
JP2003172230A (ja) * 2001-12-03 2003-06-20 Nachi Fujikoshi Corp 高圧プランジャポンプの強制潤滑装置
DE10200792A1 (de) * 2002-01-11 2003-07-31 Bosch Gmbh Robert Kraftstoffpumpe für eine Brennkraftmaschine
US7513756B2 (en) * 2002-10-29 2009-04-07 Bosch Automotive Systems Corporation Fuel supply pump and tappet structure body
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JP3693992B2 (ja) * 2002-11-08 2005-09-14 三菱電機株式会社 高圧燃料ポンプ
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JP5372692B2 (ja) * 2009-10-06 2013-12-18 日立オートモティブシステムズ株式会社 高圧燃料ポンプ
JP5592143B2 (ja) * 2010-04-09 2014-09-17 ヤンマー株式会社 燃料噴射ポンプ
JP5390705B2 (ja) * 2010-06-11 2014-01-15 ボッシュ株式会社 燃料供給ポンプ
DE102010041002A1 (de) * 2010-09-20 2012-03-22 Robert Bosch Gmbh Hochdruckpumpe

Also Published As

Publication number Publication date
US20150118066A1 (en) 2015-04-30
JP2015519507A (ja) 2015-07-09
EP2660459A1 (fr) 2013-11-06
CN104508292A (zh) 2015-04-08
KR20150004415A (ko) 2015-01-12
WO2013164220A1 (fr) 2013-11-07
CN104508292B (zh) 2017-03-15
KR101629903B1 (ko) 2016-06-13
JP6185985B2 (ja) 2017-08-23

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