EP3064759B1 - Déflecteur de combustible à température élevée pour un ensemble d'entraînement de pompe à carburant - Google Patents

Déflecteur de combustible à température élevée pour un ensemble d'entraînement de pompe à carburant Download PDF

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Publication number
EP3064759B1
EP3064759B1 EP16153708.9A EP16153708A EP3064759B1 EP 3064759 B1 EP3064759 B1 EP 3064759B1 EP 16153708 A EP16153708 A EP 16153708A EP 3064759 B1 EP3064759 B1 EP 3064759B1
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EP
European Patent Office
Prior art keywords
plunger
tappet
fuel
spring seat
fuel pump
Prior art date
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EP16153708.9A
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German (de)
English (en)
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EP3064759A1 (fr
Inventor
James McHattie
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Delphi Technologies IP Ltd
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Delphi Technologies IP Ltd
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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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • 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
    • F04B1/0408—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
    • 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
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • 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

Definitions

  • This invention relates to a drive assembly for a fuel pump.
  • the invention relates to a drive assembly for a high pressure fuel pump and more specifically to a drive assembly including a deflector configured to shield components of the fuel pump from unwanted exposure to hot, high pressure fuel.
  • a tappet In this arrangement it is typical for a tappet to be provided to transmit drive from the cam and a cam rider, to each of the plungers.
  • 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.
  • Each tappet is located within a tappet bore provided in the pump housing and is arranged so that, as the cam is driven, each tappet is caused to reciprocate within its respective bore, resulting in reciprocating motion to the respective plunger.
  • the tappet As the tappet is driven radially outward from the cam shaft by the cam rider, its respective plunger is driven to reduce the volume of the pumping chamber.
  • This part of the pumping cycle is referred to as the pumping stroke of the plunger, during which fuel within the associated pumping chamber is pressurised to a relatively high level.
  • the plunger is urged in a radially inward direction toward the cam under the influence of a plunger return spring.
  • a secondary function of the tappet is to reduce lateral forces applied to the plunger by transmitting transverse loads to the tappet bore so that generally the plunger is driven in a reciprocal motion by the tappet along a respective longitudinal axis of motion.
  • a known tappet which is slidably received in a tappet bore in the pump housing, is generally cup-shaped and has a cylindrical side wall portion to cooperate with the wall of the tappet bore, and a base end portion opposing the cam rider, which together define an internal chamber.
  • Vents or windows may be provided in the base portion and/or side wall portion of the tappet to allow a lubricating fluid to flow from a region around the cam mechanism (the "lower cam box”) to a region within the tappet (the “upper cam box”) so that hydraulic forces do not inhibit sliding movement of the tappet within the tappet bore.
  • a spring seat or plate is mounted to or otherwise engaged with the lower end of the plunger and is received in the upper cam box.
  • a plunger return spring abuts the radially outer face of the spring seat and is compressed during a pumping stroke of the plunger, so that a return biasing force is applied to the plunger, via the spring seat, to help drive the plunger return stroke.
  • a coupling mechanism in the form of a circlip may be used to couple the bucket tappet to the lower portion of the pumping plunger, so that axial motion of one (e.g., the tappet) results in axial motion of the other (e.g., the plunger).
  • High pressure fuel pumps using a rider/tappet arrangement may allow hot fuel to leak between the plunger and plunger bore and toward the plunger-tappet interfaces, particularly during the pumping stroke.
  • the leakage can be considerable.
  • hot fuel under pressure, may be directed at the interfaces during the pumping stroke, transferring additional heat from the hot fuel to the interfaces and/or promoting wear to occur at the interfaces. Accordingly, the present invention seeks to address at least one of the aforementioned problems in the art.
  • the invention provides a spring seat including a fuel deflector surface for a fuel pump assembly configured to shield sensitive parts from high pressure, high temperature leakage fuel generated during a pumping stroke.
  • the fuel deflector surface is configured to cause the leaked fuel to take a longer flow path from the upper cam box to the lower cam box and thereby increase mixing and cooling of the leaked fuel with that resident within the lower cam box.
  • a spring seat for use in a high pressure fuel pump assembly.
  • the fuel pump assembly further includes a pump housing, a pump head, a tappet, a plunger, and a return spring.
  • the pump housing includes at least one bore for receiving a corresponding number of tappets.
  • the pump head includes a plunger bore, the plunger is driven in a reciprocal manner within the plunger bore by a drive arrangement to pressurise fuel disposed within a pumping chamber defined by the pump head and the plunger.
  • the tappet includes at least one vent and is operably disposed between the drive arrangement and the plunger.
  • the spring seat is coupled with the plunger. The plunger may be positioned within an aperture formed in the spring seat.
  • the spring seat is disposed within an upper cam box defined within the tappet.
  • the return spring is disposed between the spring seat and the pump head to bias the plunger against the tappet at an interface.
  • the spring seat is characterised by a deflector surface configured to direct high temperature fuel outwardly through the at least one vent from the upper cam box to a lower cam box, wherein the spring seat is coupled with the plunger at a distance from the interface between the plunger and the tappet along a longitudinal axis of the plunger to thereby limit the effects of high pressure fuel within the fuel pump assembly.
  • the spring seat is be coupled with the plunger at a distance of approximately 3.0mm to 4.0mm from the interface between the plunger and the tappet.
  • the deflector surface on the spring seat may further include an annularly tapered portion that is directed toward the upper cam box and inwardly toward the plunger to form an acute angle relative to a longitudinal axis of the plunger.
  • the spring seat may include an outer diameter, the tappet includes an inner diameter, and wherein the outer diameter of the spring seat is less than the inner diameter of the tappet and closely matched with the inner diameter of the tappet.
  • the tappet may include a base portion and a side wall portion.
  • the base portion includes a perimeter, the side wall portion is connected with the base portion so as to be upstanding from a perimeter of the base portion.
  • the side wall portion is slidably disposed within the bore, and the side wall portion and the base portion defines the upper cam box.
  • the base portion is configured for cooperating with the drive arrangement for driving the plunger in the reciprocal manner.
  • At least one of the base portion or the side wall portion are provided with of the at least one vent for allowing the passage of fuel from the upper cam box to the lower cam box.
  • the fuel pump assembly may further comprise a cam rider, wherein the cam rider is operationally disposed between the drive arrangement and the tappet.
  • the fuel pump assembly includes a pump housing, a pump head, a tappet, a plunger, a spring seat, and a return spring.
  • the pump housing includes a bore for receiving the tappet.
  • the pump head includes a plunger bore.
  • the plunger is configured for being driven in a reciprocal manner within the plunger bore by a drive arrangement to pressurise fuel disposed within a pumping chamber defined by the pump head and the plunger.
  • the tappet includes at least one vent and is operably disposed between the drive arrangement and the plunger.
  • the spring seat is coupled with the plunger and disposed within an upper cam box defined within the tappet.
  • the return spring is disposed between the spring seat and the pump head to bias the plunger against the tappet at an interface.
  • the method is characterised by: providing a deflector surface on the spring seat that is configured to direct high temperature fuel outwardly through the at least one vent from the upper cam box to a lower cam box as the plunger is driven in the reciprocal manner, and positioning the spring seat with respect to the plunger at a distance from the interface between the plunger and the tappet along a longitudinal axis of the plunger to thereby limit the effects of high pressure fuel within the fuel pump assembly.
  • the spring seat comprises a deflector surface configured to force the high pressure leakage to take a longer flow path (and therefore provide more cooling/mixing time) before reaching sensitive moving parts and the interfaces between them.
  • the fuel pump assembly 10' having a rider/tappet arrangement is shown.
  • the fuel pump assembly 10' includes a pump housing 12' provided with an axially extending opening 14'. Opening 14' extends in a direction into the page shown in Figure 5 .
  • a cam shaft (not shown) having an axis of rotation 16' drives a drive arrangement such as an eccentrically mounted cam 18' mounted in opening 14'.
  • Pump housing 12' is provided with first, second and third radially extending openings or through bores 20a', 20b', 20c', each of which communicates at a radially inner end 21' thereof with axially extending opening 14' which extends through housing 12'.
  • Other numbers of through bores can of course be utilised according to certain other embodiments of the present invention.
  • a radially outer end 23' of each housing bore 20a', 20b', 20c' receives a respective pump head 22a', 22b', 22c'.
  • Each pump head 22a', 22b', 22c' may be substantially identical and therefore for illustrative purposes, reference will be made hereinafter only to pump head 22a' shown in Figure 5 .
  • Pump head 22a' includes a head portion 24' and a radially inwardly extending head turret 26' which projects into outer end 23' of opening 14' in pump housing 12'.
  • Head turret 26' is provided with a plunger bore 28' that is configured for slidably receiving a pumping plunger 30'.
  • a blind end 32' of plunger bore 28' is located within head portion 24' of pump head 22a' where at least one valve 33' is located to allow fluid communication into and out of a pumping chamber 34'.
  • Blind end 32' of plunger bore 28' defines, together with a radially outer end face 36' of plunger 30', pumping chamber 34'.
  • Pumping plunger 30' is an elongate shaft-like member that slides within plunger bore 28' inward toward and outward away from blind end 32' of pumping chamber 34' (the "pumping cycle").
  • the volume of pumping chamber 34' reduces.
  • the volume of pumping chamber 34' increases.
  • fuel at relatively low pressure is received during the return stroke of the plunger 30', and pressurisation of fuel to a relatively high level suitable for injection takes place as plunger 30' is driven to perform the pumping stroke upon rotation of the cam shaft.
  • Tappet 40' is a substantially hollow body including a side wall portion 42' and a base portion 44'.
  • Side wall portion 42' is generally cylindrical and extends upwardly from base portion 44' at the perimeter 45' of base portion 44' so as to define a generally bucket-shaped member.
  • Base portion 44' and side wall portion 42' may be separately or integrally formed.
  • An upper lip 48' of side wall portion 42' forms the circular surface which is urged upwards towards head portion 24' during the pumping stroke.
  • Base portion 44' provides a blind end of an internal chamber or upper cam box 50' defined within tappet 40'.
  • Tappet 40' is located within radially inner end 21' of housing bore 20a' so that an internal surface of housing bore 20a' is in sliding contact with cylindrical side wall portion 42' and serves to guide longitudinal movement and constrain lateral movement of tappet 40'.
  • Tappet 40' is shaped in the form of a bucket and may be referred to as a "bucket tappet.”
  • Tappet 40' is coupled to plunger 30' by suitable means so that relative longitudinal movement is transferred between plunger 30' and tappet 40'. Accordingly, spring seat 54' in the form of a plate is received by a lower end of plunger 30' in an interference fit. While spring seat 54' is described as being secured to the end of plunger 30' by an interference fit, it will be appreciated that spring seat 54' could alternatively be integrally formed with the shaft-like plunger 30' or could be secured thereto via other ways. Spring seat 54' and plunger 30' move together as one unit.
  • Spring seat 54' locates one end of return spring 56' and the other end of plunger return spring 56' abuts a radially inner surface 57' of head portion 24' of pump head 22a', so that return spring 56' serves to apply a return biasing force to spring seat 54' and plunger 30' (and hence also to the tappet), to drive the plunger return stroke.
  • vents or through holes 52' are formed circumferentially around side wall portion 42' and/or base portion 44' of tappet 40' to enable fluid, such as engine fuel, to flow between an outer region surrounding tappet 40' and an inner region within upper cam box 50'.
  • Vents 52' reduce the pressure differential between upper cam box 50' and opening 14' within lower cam box 51' and therefore prevent excessive hydraulic force on tappet 40' during reciprocating motion.
  • Vents 52' may be, for example, circular or church window style or the like.
  • the cam shaft co-operates with the eccentrically mounted cam 18' and a generally tubular cam rider 60' which extends coaxially with cam 18'.
  • first 62a', second 62b' and third 62c' flattened surfaces referred to as flats.
  • Each one of flats 62a', 62b', 62c' co-operates with base portion 44' of tappet 40' for a respective one of plungers 30'.
  • respective tappets 40' are operably coupled to respective plungers 30'
  • rotation of the cam shaft causes cam rider 60' to ride over the surface of eccentrically mounted cam 18' thereby imparting drive to both each respective tappet 40' and plunger 30' combination.
  • plunger 30' As the tappet 40' and plunger 30' are driven through the pumping stroke, low pressure fuel within pumping chamber 34' is compressed by plunger 30'. Compression of the fuel within pumping chamber 34' causes the fuel to increase in fluid pressure as well as increase in temperature. Because plunger 30' is slidably engaged within plunger bore 28', at least some gap is present between plunger 30' and plunger bore 28'. As a result, high temperature fuel, under pressure, is able to leak around plunger 30' and is directed toward spring seat 54' and base portion 44', and an interface 55' between plunger 30' and base portion 44' and an interface 59' between tappet 40' and cam rider 60' ( Figure 5 ), before passing through vents 52' and into lower cam box 51'.
  • alleviation of the adverse effects of high temperature fuel under pressure may be accomplished via a high temperature fuel deflector surface and a modified fuel flow path generally comprising a tappet 40', spring seat 54' and return spring 56'.
  • Spring seat 54' has a larger outer diameter 70' than the prior art spring seat 54, to more closely match an inner diameter 72' of tappet 40' (i.e. the outer diameter 70' of the spring seat 54' is marginally smaller than the inner diameter 72' of the tappet 40'), so as to limit the passage of leaked, high temperature fuel between the diameters 70', 72' during the pumping stroke.
  • Spring seat 54' is also positioned on plunger 30' an extended distance 74' from interface 55', as opposed to the spring seat 54 of the prior art ( Figure 3 ) which is essentially flush with interface 55.
  • distance 74' may be approximately 3.0mm to 4.0mm.
  • spring seat 54' may include deflector surface 58' proximate return spring 56'. Deflector surface 58' may further include an annularly tapered portion 64' which may be used to direct high temperature fuel outwardly through plunger tappet vents 52' and the lower cam box 51' during the pumping stroke.
  • Annularly tapered portion 64' may be directed toward upper cam box 50' and inwardly toward plunger 30' so as to form an acute angle relative to a longitudinal axis 76' of plunger 30'.
  • Vents 52' may be elongated from base portion 44' toward pumping chamber 34' to receive the redirected high temperature fuel for passage therethrough.
  • the elevated spring seat 54' in combination with deflector surface 58', operate to shield or limit the interfaces 55' and 59' from exposure to high temperature fuel.
  • vents 52' (described below) to be mixed and cooled in lower cam box 51' before returning to upper cam box 50' during the return stroke, as generally shown by arrow B.
  • the modified tappet 40' of the present invention is a substantially hollow body including a side wall portion 42' and a base portion 44'.
  • Side wall portion 42' is generally cylindrical and extends upwardly from base portion 44' at the perimeter 45' of base portion 44' so as to define a generally bucket-shaped member.
  • Side wall portion 42' includes one or more vents or through holes 52'.
  • vents 52' are extended toward upper lip 48' of side wall portion 42', so as to be essentially in alignment with deflector surface 58', or even extend further upward toward upper lip 48', when the pumping plunger 30' reaches the terminal point of the pumping stroke, so as to form a direct path for the fuel to flow from the angled portion 64' of the deflector surface 58, through the extended vent(s) 52' and to the lower cam box 51'.
  • the high pressure, high temperature fuel may be directed through vents 52' by deflector surface 58' to provide for additional cooling and mixing of the leaking fuel with that fuel resident within lower cam box 51'.
  • cooler fuel may then lubricate and cool interfaces 55' and 59', and other surrounding components.

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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)

Claims (8)

  1. Assemblage de pompe à carburant (10') comprenant un siège de ressort (54'), l'assemblage de pompe à carburant (10') incluant en outre un carter de pompe (12'), une tête de pompe (22a', 22b', 22c'), un poussoir (40'), un piston (30') et un ressort de rappel (56'), le carter de pompe (12') incluant un perçage (20a', 20b', 20c') destiné à recevoir le poussoir (40'), la tête de pompe (22a', 22b', 22c') incluant un perçage à piston (28'), le piston (30') étant entraîné dans une manière de va-et-vient à l'intérieur du perçage à piston (28') via un agencement d'entraînement (18') pour pressuriser du carburant disposé à l'intérieur d'une chambre de pompage (34') définie par la tête de pompe (22a', 22b', 22c') et le piston (30'), le poussoir (40') incluant au moins un évent (52') pour permettre le passage de carburant depuis le carter à came supérieur (50') jusqu'à un carter à came inférieur (51') formé circonférentiellement autour d'une portion formant paroi latérale (42') et/ou d'une portion de base (44') du poussoir (40') et étant disposé de manière fonctionnelle entre l'agencement d'entraînement (18') et le piston (30'), le siège de ressort (54') étant couplé au piston (30') et disposé à l'intérieur de la portion formant paroi latérale (42') et la portion de base (44') définissant un carter à came supérieur (50') défini à l'intérieur du poussoir (40'), le ressort de rappel (56') étant disposé entre le siège de ressort (54') et la tête de pompe (22a', 22b', 22c') pour solliciter le piston (30') contre le poussoir (40') au niveau d'une interface (55'),
    caractérisé en ce que le siège de ressort (54') comprend une surface de déflecteur (58') incluant une portion effilée de manière annulaire (64') qui est utilisée pour diriger du carburant à haute température vers l'extérieur à travers des évents de poussoir de piston (52') et le carter à came inférieur (51') pendant la course de pompage, et
    dans lequel le siège de ressort (54') est couplé au piston (30') à une distance (74') de l'interface (55') entre le piston (30') et le poussoir (40') le long d'un axe longitudinal (76') du piston (30'), la distance (74') étant entre 3,0 mm et 4,0 mm.
  2. Assemblage de pompe à carburant (10') selon la revendication 1, dans lequel la portion effilée de manière annulaire (64') est dirigée en direction d'un carter à came supérieur (50') et vers l'intérieur en direction du piston (30') pour former un angle aigu par rapport à un axe longitudinal (76') du piston (30').
  3. Assemblage de pompe à carburant (10') selon l'une quelconque des revendications précédentes, dans lequel le siège de ressort (54') inclut un diamètre extérieur (70'), dans lequel le poussoir (40') inclut un diamètre intérieur (72'), dans lequel le diamètre extérieur (70') du siège de ressort (54') est inférieur au diamètre intérieur (72') du poussoir (40').
  4. Assemblage de pompe à carburant (10') selon la revendication 3, dans lequel le diamètre extérieur (70') du siège de ressort (54') est intimement apparié au diamètre intérieur (72') du poussoir (40').
  5. Assemblage de pompe à carburant (10') selon l'une quelconque des revendications précédentes, dans lequel le siège de ressort (54') est doté d'une ouverture destinée à recevoir le piston (30').
  6. Assemblage de pompe à carburant (10') selon l'une quelconque des revendications précédentes, dans lequel le carter de pompe (12') est doté d'une pluralité de perçages (20a', 20b', 20c'), et dans lequel un nombre correspondant de poussoirs (40') sont disposés dans les perçages respectifs (20a', 20b', 20c').
  7. Assemblage de pompe à carburant (10') selon l'une quelconque des revendications précédentes, dans lequel l'assemblage de pompe à carburant (10') inclut en outre un suiveur de came (60') disposé de manière fonctionnelle entre l'agencement d'entraînement (18') et le poussoir (40').
  8. Procédé destiné à protéger des composants à l'intérieur d'une pompe à carburant à haute pression (10') selon l'une des revendications 1 à 7, le procédé comprenant
    une étape consistant à fournir une surface de déflecteur (58') sur ledit siège de ressort (54') qui est configurée pour diriger un carburant à haute température à travers ledit au moins un évent (52') depuis le carter à came supérieur (50') jusqu'à un carter à came inférieur (51') quand le piston (30') est entraîné dans une manière de va-et-vient, et,
    une étape consistant à positionner le siège de ressort (54') par rapport au piston (30') à une distance (74') depuis l'interface (55') entre le piston (30') et le poussoir (40') le long d'un axe longitudinal (76') du piston (30') pour ainsi limiter les effets du carburant à haute pression à l'intérieur de l'assemblage de pompe à carburant (10').
EP16153708.9A 2015-03-03 2016-02-01 Déflecteur de combustible à température élevée pour un ensemble d'entraînement de pompe à carburant Active EP3064759B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB201503556A GB201503556D0 (en) 2015-03-03 2015-03-03 High temperature fuel deflector for a fuel pump drive assembly

Publications (2)

Publication Number Publication Date
EP3064759A1 EP3064759A1 (fr) 2016-09-07
EP3064759B1 true EP3064759B1 (fr) 2020-09-02

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GB (1) GB201503556D0 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2570290B (en) * 2018-01-09 2020-04-29 Delphi Tech Ip Ltd Fuel pump

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Publication number Priority date Publication date Assignee Title
DE19753593A1 (de) * 1997-12-03 1999-06-17 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
WO2004040128A1 (fr) * 2002-10-31 2004-05-13 Robert Bosch Gmbh Pompe haute pression d'alimentation en carburant comprenant un clapet a bille dans l'admission basse pression
DE102006038839A1 (de) * 2006-08-18 2008-02-21 Robert Bosch Gmbh Hochdruckpumpe für ein Kraftstoffsystem einer Brennkraftmaschine
DE102012210199A1 (de) * 2012-06-18 2013-12-19 Robert Bosch Gmbh Stößelbaugruppe für eine Kraftstoffhochdruckpumpe sowie Kraftstoffhochdruckpumpe

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GB201503556D0 (en) 2015-04-15
EP3064759A1 (fr) 2016-09-07

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