EP3085944B1 - Tête de poussoir à ressort extérieur avec guide de tourelle pour une pompe à carburant - Google Patents
Tête de poussoir à ressort extérieur avec guide de tourelle pour une pompe à carburant Download PDFInfo
- Publication number
- EP3085944B1 EP3085944B1 EP16163743.4A EP16163743A EP3085944B1 EP 3085944 B1 EP3085944 B1 EP 3085944B1 EP 16163743 A EP16163743 A EP 16163743A EP 3085944 B1 EP3085944 B1 EP 3085944B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- plunger
- tappet
- pumping
- base portion
- return spring
- 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.)
- Active
Links
- 239000000446 fuel Substances 0.000 title claims description 40
- 238000005086 pumping Methods 0.000 claims description 83
- 238000000034 method Methods 0.000 claims description 13
- 239000012530 fluid Substances 0.000 claims description 10
- 238000004891 communication Methods 0.000 claims description 3
- 230000000712 assembly Effects 0.000 claims description 2
- 238000000429 assembly Methods 0.000 claims description 2
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 230000001050 lubricating effect Effects 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 239000000654 additive Substances 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Classifications
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- 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
- 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
- F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
- F02M59/06—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
-
- 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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
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- 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
- 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
- F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
Definitions
- This invention relates to an intermediate drive assembly for a fuel pump.
- the invention relates to a spring actuated tappet and more specifically to a spring actuated tappet having an internal plunger spring and an externally mounted tappet spring seated on a tappet flange.
- a known common rail fuel pump for example as described in US2421844 , or in European Patent No. EP 1184568 , three pumping plungers are arranged at equi-angularly spaced locations around an engine driven cam.
- the cam carries a cam ring (or cam rider), which travels over the surface of the cam as it is driven by the engine.
- Each plunger is mounted within a respective plunger bore provided in a pump housing and, as the cam is driven, each of the plungers is caused to reciprocate within its bore. As the plungers reciprocate, each causes pressurisation of fuel within an associated pumping chamber.
- the delivery of fuel from the pumping chambers to a common high pressure supply passage is controlled by means of respective delivery valves associated with each of the pumps.
- the high pressure supply passage supplies fuel to a common rail, or other accumulator volume, for delivery to the downstream injectors of the injection system.
- an intermediate drive member in the form of a tappet to be provided to transmit drive from the cam/cam rider arrangement 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 plungers.
- the tappet is driven radially outward from the 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 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 to a region within the tappet 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 internal chamber of the tappet.
- 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).
- the internal spring employed within current systems limits the size of the spring that can be used within the pump.
- a larger size spring would require a larger tappet to encircle such a spring.
- this larger tappet would have an increased mass which in turn would require an even larger spring to produce the necessary biasing force during operation.
- a further drawback due to the limited size of the spring used within the pump is that it limits the size of the pumping chamber and thus establishes a maximum pressure ceiling for the pump.
- the present invention seeks to address at least one of the aforementioned problems in the art.
- the invention provides an intermediate drive assembly for a fuel pump having improved tappet performance and reduced manufacturing costs.
- rider/tappet type fuel pumps use a guided tappet to protect the pumping plunger (pumping element) from the side-load of the orbiting cam rider of a drive arrangement.
- the side-loading of the tappet occurs due to friction between the cam rider and tappet.
- Traditional designs utilise a spring inside the tappet which ensures contact between the tappet and cam rider during the pumping operation.
- the spring rests on a spring seat which is press-fit onto the plunger such that the spring also maintains the contact between the plunger and tappet.
- This arrangement requires the tappet return spring to fit within the tappet, and as a result, is limited in the diameter that can be used. For instance, a larger spring would require a larger tappet (which would have more mass), which would in turn require a still larger spring to provide sufficient restorative force to the higher mass tappet.
- the invention therefore provides an intermediate drive assembly having an externally sprung tappet.
- the tappet is flanged at a cambox end to provide a spring seat for a larger-diameter tappet return spring.
- This spring wraps around the outside of the tappet and can be of a much larger diameter than the tappet, if required.
- a second, plunger return spring is fitted between a head turret and the plunger spring seat in order to maintain contact between the plunger and the tappet.
- the plunger return spring is sized only to act against the lighter weight plunger and not the heavier tappet.
- a tappet guide may then be machined on the outer diameter of the head turret, thereby removing the need for a honing operation or sleeving to form the tappet guide in the pump housing. Further, since the plunger is not directly connected to the tappet, the allowable coaxial tolerance between plunger bore and machined outer diameter of the head turret may be increased. The resulting improvements include a greater range of spring design options, the possibility for increasing the size of the head turret (for higher pressure operation) and eliminating the need for sleeving or machining of the pump housing to form the tappet guide.
- an intermediate drive assembly for a fuel pump assembly including a pump housing provided with a bore for receiving the intermediate drive assembly.
- the fuel pump assembly further includes a pumping plunger and a pump head.
- the pump head includes a pump head portion and a head turret extending into the bore.
- a plunger bore is defined in the pump head and extends within the head turret.
- the pumping 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 pumping plunger.
- the intermediate drive assembly is operably disposed between the drive arrangement and the pumping plunger and comprises: a tappet including a base portion and a side wall portion.
- the base portion includes a perimeter, and the side wall portion is connected with the base portion so as to be upstanding an intermediated distance from the perimeter of the base portion to define a tappet flange.
- the side wall portion is slidably disposed around the head turret.
- the side wall portion and base portion define an internal chamber.
- the base portion is configured for cooperating with the drive arrangement for driving the pumping plunger in the reciprocal manner.
- a plunger spring seat is coupled to the pumping plunger and positioned within the internal chamber.
- the invention in this is aspect is characterised in that a plunger return spring is positioned within the internal chamber and disposed between the plunger spring seat and the head turret for biasing the pumping plunger away from the pump head.
- a tappet return spring is positioned around the side wall portion and disposed between the tappet flange and the pump head portion for biasing the tappet away from the pump head.
- the intermediate drive assembly of the invention may also include a pumping plunger, wherein the plunger spring seat is provided with an aperture for receiving the pumping plunger.
- the aperture in the plunger spring seat may be coupled with a lower end of the pumping plunger using a press fit or friction fit.
- the intermediate drive assembly may also include a plurality of vents defined in at least one of the base portion or the side wall portion of the tappet for allowing the passage of fluid.
- the intermediate drive assembly may further include at least one valve in fluid communication with the plunger chamber.
- the pump housing of the intermediate drive assembly may be provided with a plurality of bores, wherein a corresponding number of intermediate drive assemblies are disposed in the respective bores.
- the intermediate drive assembly may have a side wall portion that is generally cylindrical-shaped.
- the plunger spring seat of the intermediate drive assembly may be integrally formed with the pumping plunger.
- the invention further provides a method for maintaining a pumping plunger in operational engagement with a drive arrangement in a fuel pump assembly.
- the fuel pump assembly includes a pump housing provided with a bore.
- the fuel pump assembly includes the pumping plunger and a pump head.
- the pump head includes a pump head portion and a head turret extending into the bore.
- a plunger bore is defined in the pump head and extends within the head turret.
- the pumping plunger is configured for being driven in a reciprocal manner within the plunger bore by the drive arrangement to pressurise fuel disposed within a pumping chamber defined by the pump head and the pumping plunger.
- the method comprises: providing a tappet including a base portion and a side wall portion.
- the base portion includes a perimeter, and the side wall portion is connected with the base portion so as to be upstanding an intermediated distance from the perimeter of the base portion to define a tappet flange.
- the side wall portion is configured for being slidably disposed around the head turret, the side wall portion and the base portion defining an internal chamber.
- the method further comprises providing a plunger spring seat that is coupled to the pumping plunger wherein the plunger spring seat is positioned within the internal chamber.
- the method is characterised by positioning a plunger return spring within the internal chamber and disposing the plunger return spring between the plunger spring seat and the head turret; positioning a tappet return spring around the side wall portion and disposing the tappet return spring between the tappet flange and the pump head portion; urging the pumping plunger against base portion using the plunger return spring; and urging the base portion against the drive engagement using the tappet return spring thereby transmitting movement of the drive engagement to reciprocate the pumping plunger.
- the method may also include selecting a ratio of spring strengths of the tappet return spring and the plunger return spring such that a first biasing force exerted by the tappet return spring on the tappet flange and a second biasing force exerted by the plunger return spring on the pumping plunger maintains the plunger in contact with the base portion during reciprocating movement.
- the intermediate drive assembly comprises a tappet having an external flange configured to mount a tappet return spring wherein the tappet also defines an internal chamber configured to house a plunger return spring.
- the intermediate drive assembly allows for less precise machining due to larger plunger bore/turret outer diameter coaxial tolerances.
- the intermediate drive assembly may also accommodate enlargement of the head turret diameter for higher pressure applications while requiring no changes to the pump housing.
- the fuel pump assembly 10 includes a pump housing 12 provided with an axially extending opening 14. The opening extends in the direction into the page shown in Figure 1 .
- a cam shaft (not shown) having an axis of rotation 16 drives a drive arrangement 18, such as, for example, an eccentrically mounted cam mounted in opening 14.
- Pump housing 12 is provided with a first, second and third radially extending openings or through bores 20a, 20b, 20c, each of which communicates at a radially inner end thereof with axially extending opening 14 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 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 1 , which is described and shown in the further drawings.
- 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 pumping chamber 34.
- Blind end 32 of plunger bore 28 defines, together with a radially outer end face 36 of plunger 30, the pumping chamber 34.
- Plunger 30 is an elongate shaft-like member that slides within plunger bore 28 inward toward and outward away from pumping chamber 34 (the "pumping cycle"). As outer end face 36 of plunger 30 moves toward pumping chamber 34 in the direction shown by arrow A in Figure 3 (the “pumping stroke”), the volume of the pumping chamber 34 reduces. As plunger 30 moves away from the pumping chamber 34 in the direction along the axis of movement opposite to the direction shown by arrow A in Figure 3 (the "return stroke”), the volume of the pumping chamber 34 increases.
- Head turret 26 of pump head 22a provides an increased sealing length for plunger bore 28, which tends to reduce high pressure fuel leakage from pumping chamber 34 along a path between plunger 30 and plunger bore 28.
- 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 upstandingly from base portion 44 at an intermediated distance from a perimeter 45 of base portion 44 so as to define a generally circular or disc-shaped radially extended tappet flange 46.
- 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.
- An internal chamber 50 within tappet 40 is defined by side wall portion 42 and base portion 44.
- Base portion 44 provides a blind end of internal chamber 50.
- Tappet 40 locates within radially inner end 21 of opening 14 (see Figure 1 ) so that an internal surface 51 of side wall portion 42 is in sliding contact with an external surface 53 of turret 26 and serves to guide longitudinal movement and constrain lateral movement of tappet 40 during the pumping and return strokes.
- One or more 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 from an outer region surrounding tappet 40 to an inner region within internal chamber 50. Vents 52 reduce the pressure differential between internal chamber 50 and opening 14 and therefore prevent excessive hydraulic force on tappet 40 during reciprocating motion.
- Vents 50 may be, for example, circular or church window style or the like. Additionally, while four vents are shown in the Figures, it will be appreciated that other shapes and numbers of openings are possible according to certain other embodiments of the present invention.
- Tappet 40 is coupled to plunger 30 by multiple springs so that plunger 30 is urged to remain in contact with tappet 40 during the pumping cycle.
- a plunger spring seat 54 in the form of a plate is received in internal chamber 50 of tappet 40 and defines a central aperture 55 for receiving a lower end of plunger 30 in a press or friction interference fit. While plunger 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. Plunger spring seat 54 and plunger 30 move together as one unit.
- Plunger spring seat 54 locates one end of a plunger return spring 56 with the other end of plunger return spring 56 abutting a radially inner surface 57 of head turret 26 of pump head 22a, so that plunger return spring 56 serves to apply a return biasing force to plunger spring seat 54 and plunger 30 to drive a plunger return stroke.
- a second tappet return spring 58 has one end located on a top surface 59 of tappet flange 46 with the second end abutting against a radially inner surface 61 of head portion 24 of pump head 22a. Tappet return spring 58 may be concentrically disposed within plunger return spring 56.
- Tappet return spring 58 serves to apply a return biasing force to tappet flange 46 (and therefore tappet 38) during a plunger (and therefore tappet) return stroke.
- the tappet return spring 58 biases tappet 38 away from pump head 22a during the return stroke while plunger return spring 56 urges plunger 30 against tappet 40 so that plunger 30 is urged to be in contact with tappet 40 and a full plunger stroke is travelled upon rotation of cam 18 or rider 60 located on cam 18.
- the cam shaft co-operates with the eccentrically mounted cam 18 and, as shown in Figure 1 , the co-operable generally tubular cam rider 60 which extends coaxially with cam 18.
- cam rider 60 On the outer surface cam rider 60 is provided with 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 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.
- a lubricating fluid such as fuel or the like, is provided in opening 14 of the housing and bore 20 in which tappet 40 slides to reduce wear due to friction.
- tappet 40 is caused to reciprocate in its respective bore (e.g., 20a as described above) and plunger 30 is caused to reciprocate within plunger bore 28. There is thus a first reciprocating motion of tappet 40 within the housing bore and a further reciprocating motion of plunger 30 within plunger bore 28.
- Tappet 40 and plunger 30 are thus driven together causing plunger 30 to perform a pumping cycle including a pumping stroke during which tappet 40 and plunger 30 are driven radially outward from the central cam shaft (i.e., in the direction shown by Arrow A in Figure 3 ; towards the respective pump head) which reduces the volume within pumping chamber 34.
- plunger 30 is driven toward head portion 24 of pump head 22a within its plunger bore 28 and fuel within pumping chamber 34 is pressurised to a high level.
- tappet 40 and plunger 30 are urged in a radially inward direction, i.e. towards the centre of housing 12 and away from head portion 24 (i.e., in the direction opposite Arrow A).
- This return motion is caused by virtue of the resilient nature of tappet return spring 58 which thus biases tappet 40 away from head portion 24.
- plunger return spring 56 biases plunger 30 away from valve 33.
- plunger 30 is urged outwardly from plunger bore 28 and held in contact with tappet 40, and fuel at relatively low pressure may be allowed to fill the associated pumping chamber 34 via valve 33.
- the ratio of spring strengths of tappet return spring 58 and plunger return spring 56 is selected such that the biasing forces exerted by tappet return spring 58 on tappet 40 and plunger return spring 56 on plunger 30 are closely matched so that plunger 30 return is generally synchronous with tappet 40 return.
- plunger return spring 56 may be selected to store a slightly larger biasing force than tappet return spring 58. In this manner, when plunger 30 is urged by plunger return spring 56 to perform its return stroke, this addition biasing force ensures that plunger 30 travels with tappet 40 and that contact is maintained between tappet 40 and the flat of cam rider 60 and that plunger 30 fully return travels during the pumping cycle.
- Coupled is used to indicate either a direct connection between two components or, where appropriate, an indirect connection to one another through intervening or intermediate components. In contrast, if a component is referred to as being “directly coupled” to another component, there are no intervening elements present.
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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 (10)
- Assemblage d'entraînement intermédiaire (38) pour un ensemble formant pompe à carburant (10), l'ensemble formant pompe à carburant (10) incluant un boîtier de pompe (12) doté d'un perçage (20a, 20b, 20c) pour recevoir l'assemblage d'entraînement intermédiaire (38), l'ensemble formant pompe à carburant (10) incluant en outre un piston de pompage (30) et une tête de pompe (22a, 22b, 22c), la tête de pompe (22a, 22b, 22c) incluant une portion de tête de pompe (24) et un tourillon de tête (26) s'étendant dans le perçage (22a, 22b, 22c), le piston de pompage (30) étant entraîné dans un déplacement en va-et-vient à l'intérieur d'un perçage de piston (28) par 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 de pompage (30), l'assemblage d'entraînement intermédiaire (38) étant disposé fonctionnellement entre l'agencement d'entraînement (18) et le piston de pompage (30), l'assemblage d'entraînement intermédiaire (38) comprenant :un poussoir (40) incluant une portion de base (44) et une portion de paroi latérale (42), la portion de base (44) incluant un périmètre (45), la portion de paroi latérale (42) étant connectée à la portion de base (44) de manière à être dressée sur une distance intermédiaire depuis le périmètre (45) de la portion de base (44) pour définir une bride de poussoir (46), la portion de paroi latérale (42) étant disposée en coulissement autour du tourillon de tête (26), la portion de paroi latérale (42) et la portion de base (44) définissant une chambre interne (50), la portion de base (44) étant configurée pour coopérer avec l'agencement d'entraînement (18) pour entraîner le piston de pompage (30) dans le déplacement en va-et-vient ;un siège de ressort de piston (54) couplé au piston de pompage (30) et positionné à l'intérieur de la chambre interne (50) ;caractérisé par un ressort de rappel de piston (56) positionné à l'intérieur de la chambre interne (50) et disposé entre le siège de ressort de piston (54) et le tourillon de tête (26) pour solliciter le piston de pompage (30) en éloignement de la tête de pompe (22a, 22b, 22c) ; etun ressort de rappel de poussoir (58) positionné autour de la portion de paroi latérale (42) et disposé entre la bride de poussoir (46) et la portion de tête de pompe (24) pour solliciter le poussoir (40) en éloignement de la tête de pompe (22a, 22b, 22c).
- Assemblage d'entraînement intermédiaire (38) selon la revendication 1, dans lequel le siège de ressort de piston (54) est doté d'une ouverture (55) pour recevoir le piston de pompage (30).
- Assemblage d'entraînement intermédiaire (38) selon la revendication 2, dans lequel l'ouverture (55) dans le siège de ressort de piston (54) est couplée à une extrémité inférieure du piston de pompage (30) en utilisant un engagement à la presse ou un engagement à friction.
- Assemblage d'entraînement intermédiaire (38) selon l'une quelconque des revendications précédentes, dans lequel l'une au moins de la portion de base (44) ou de la portion de paroi latérale (42) est dotée d'une pluralité d'évents (52) pour permettre le passage de fluide.
- Assemblage d'entraînement intermédiaire (38) selon l'une quelconque des revendications précédentes, comprenant en outre au moins une valve (33) en communication fluidique avec la chambre de pompage (34).
- Assemblage d'entraînement intermédiaire (38) selon l'une quelconque des revendications précédentes, dans lequel le boîtier de pompe (12) est doté d'une pluralité de perçages (20a, 20b, 20c), et dans lequel un nombre correspondant d'assemblages d'entraînement intermédiaires (38) sont disposés dans les perçages respectifs (20a, 20b, 20c).
- Assemblage d'entraînement intermédiaire (38) selon l'une quelconque des revendications précédentes, dans lequel la portion de paroi latérale (42) est généralement de forme cylindrique.
- Assemblage entraînement intermédiaire (38) selon la revendication 1, dans lequel le siège de ressort de piston (54) est formé de manière intégrale avec le piston de pompage (30).
- Procédé pour maintenir un piston de pompage (30) en engagement fonctionnel avec un agencement d'entraînement (18) dans un ensemble formant pompe à carburant (10), l'ensemble formant pompe à carburant (10) incluant un boîtier de pompe (12) doté d'un perçage (20a, 20b, 20c), l'ensemble formant pompe à carburant (10) incluant le piston de pompage (30) et une tête de pompe (22a, 22b, 22c), la tête de pompe (22a, 22b, 22c) incluant une portion de tête de pompe (24) et un tourillon de tête (26) s'étendant dans le perçage (22a, 22b, 22c), le piston de pompage (30) étant configuré pour être entraîné dans un déplacement en va-et-vient à l'intérieur d'un perçage de piston (28) par l'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 par le piston de pompage (30), le procédé comprenant les étapes consistant à :fournir un poussoir (40) incluant une portion de base (44) et une portion de paroi latérale (42), la portion de base (44) incluant un périmètre (45), la portion de paroi latérale (42) étant connectée à la portion de base (44) de manière à être dressée d'une distance intermédiaire depuis le périmètre (45) de la portion de base (44) pour définir une bride de poussoir (46), la portion de paroi latérale (42) étant configurée pour être disposée en coulissement autour du tourillon de tête (26), la portion de paroi latérale (42) et la portion de base (44) définissant une chambre interne (50) ;fournir un siège de ressort de piston (54) qui est couplé au piston de pompage (50), le siège de ressort de piston (54) étant positionné à l'intérieur de la chambre interne (50) ;le procédé étant caractérisé par les opérations consistant àpositionner un ressort de rappel de piston (56) à l'intérieur de la chambre interne (50) et disposer le ressort de rappel de piston (56) entre le siège de ressort de piston (54) et le tourillon de tête (26) ;positionner un ressort de rappel de poussoir (58) autour de la portion de paroi latérale (42) et disposer le ressort de rappel de poussoir (58) entre la bride de poussoir (46) et la portion de tête de pompe (24) ;solliciter le piston de pompage (30) contre la portion de base (44) en utilisant le ressort de rappel de piston (56) ; etsolliciter la portion de base (44) contre l'agencement d'entraînement (18) en utilisant le ressort de rappel de poussoir (58) en transmettant ainsi un mouvement de l'agencement d'entraînement (38) pour déplacer en va-et-vient le piston de pompage (30).
- Procédé selon la revendication 9, comprenant en outre :
l'opération consistant à sélectionner un rapport des forces de rappel du ressort de rappel de poussoir (58) et du ressort de rappel de piston (56) de telle façon qu'une première force de sollicitation exercée par le ressort de rappel de poussoir (58) sur la bride de poussoir (46) et une seconde force de sollicitation exercée par le ressort de rappel de piston (56) sur le piston de pompage (30) maintiennent le piston de pompage (30) en contact avec la portion de base (44) pendant le déplacement en va-et-vient.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GBGB1506820.8A GB201506820D0 (en) | 2015-04-22 | 2015-04-22 | Externally sprung tappet with head turret guide for a fuel pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3085944A1 EP3085944A1 (fr) | 2016-10-26 |
EP3085944B1 true EP3085944B1 (fr) | 2019-03-27 |
Family
ID=53298980
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16163743.4A Active EP3085944B1 (fr) | 2015-04-22 | 2016-04-04 | Tête de poussoir à ressort extérieur avec guide de tourelle pour une pompe à carburant |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3085944B1 (fr) |
CN (1) | CN106065836A (fr) |
GB (1) | GB201506820D0 (fr) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2583076B (en) * | 2019-04-08 | 2021-12-22 | Delphi Tech Ip Ltd | Fuel pump plunger return spring arrangement |
CN111927664A (zh) * | 2020-08-11 | 2020-11-13 | 中国第一汽车股份有限公司 | 一种高压油泵底座及汽车 |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2421844A (en) * | 1944-01-28 | 1947-06-10 | United Aircraft Corp | Fuel injection system |
DE602006003998D1 (de) * | 2006-03-17 | 2009-01-15 | Delphi Tech Inc | Kraftstoffeinspritzpumpe |
DE102009000859A1 (de) * | 2009-02-13 | 2010-08-19 | Robert Bosch Gmbh | Kraftstoffhochdruckpumpe |
FR2998929B1 (fr) * | 2012-11-30 | 2018-08-10 | Valeo Systemes De Controle Moteur | Pompe, notamment pour l'injection de carburant dans un moteur thermique |
-
2015
- 2015-04-22 GB GBGB1506820.8A patent/GB201506820D0/en not_active Ceased
-
2016
- 2016-04-04 EP EP16163743.4A patent/EP3085944B1/fr active Active
- 2016-04-22 CN CN201610253219.1A patent/CN106065836A/zh active Pending
Non-Patent Citations (1)
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None * |
Also Published As
Publication number | Publication date |
---|---|
EP3085944A1 (fr) | 2016-10-26 |
GB201506820D0 (en) | 2015-06-03 |
CN106065836A (zh) | 2016-11-02 |
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