EP1413749A2 - Assemblage de pompe à essence - Google Patents

Assemblage de pompe à essence Download PDF

Info

Publication number
EP1413749A2
EP1413749A2 EP20030256728 EP03256728A EP1413749A2 EP 1413749 A2 EP1413749 A2 EP 1413749A2 EP 20030256728 EP20030256728 EP 20030256728 EP 03256728 A EP03256728 A EP 03256728A EP 1413749 A2 EP1413749 A2 EP 1413749A2
Authority
EP
European Patent Office
Prior art keywords
pump
fuel
shoe
pump assembly
cam
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP20030256728
Other languages
German (de)
English (en)
Other versions
EP1413749A3 (fr
EP1413749B1 (fr
Inventor
Christopher Wood
Peter A.G. Collingborn
Ian R. Thornthwaite
Daniel P. Cust
Jean Giraud
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 Technologies Inc
Original Assignee
Delphi Technologies Inc
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 Technologies Inc filed Critical Delphi Technologies Inc
Publication of EP1413749A2 publication Critical patent/EP1413749A2/fr
Publication of EP1413749A3 publication Critical patent/EP1413749A3/fr
Application granted granted Critical
Publication of EP1413749B1 publication Critical patent/EP1413749B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • 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
    • F04B1/0413—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
    • F04B1/0421—Cylinders
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/007—Cylinder heads

Definitions

  • the invention relates to a pump assembly for use in supplying high pressure fuel to the fuel injection system of a compression ignition internal combustion engine.
  • a plurality of plungers are reciprocable within respective plunger bores so as to pressurise fuel within respective pumping chambers for delivery to the fuel injection system associated with the engine. It is common to provide three plungers which are equi-angularly spaced around a drive shaft, the plungers being moveable under the influence of a cam drive arrangement.
  • the cam drive arrangement includes a common eccentric cam surface, which is cooperable with all three of the plungers to cause reciprocal movement of the plungers within their respective plunger bores in a phased, cyclical manner.
  • each of the plungers is in connection with a cylindrical tappet member which serves to drive movement of the associated plunger within its bore.
  • the tappets are slidable within tappet bores under the influence of respective roller members, driven by means of an eccentric cam surface.
  • the eccentricity of the cam surface causes the tappets, and hence the plungers, to be driven inwardly within their respective bores, the plungers thereby performing a forward or pumping stroke in which fuel within the associated pumping chamber is pressurised.
  • the tappets are urged outwardly from their associated tappet bores by means of fluid pressure within a working chamber, thus causing the respective plunger to be urged in an outward direction to perform the return stroke.
  • EP 1223334A describes a multi-plunger fuel pump in which three plungers are equi-angularly spaced around a drive shaft and driven under the influence of a reciprocable shoe and roller arrangement (a "roller-shoe” drive arrangement).
  • the roller is cooperable with the cam surface of the cam arrangement so as to impart reciprocal movement to the shoe upon rotation of the drive shaft.
  • the pump includes three pump assemblies housed within a unitary, main pump housing, each of the pump assemblies including a plunger which is slidable within a respective bore in the housing to pressurise fuel within an associated pumping chamber.
  • Inlet and outlet valves to control fuel flow to and from the pumping chambers, respectively, are provided in flow passages defined within the main pump housing.
  • a pump housing part in the form of a tubular member is arranged coaxially with the drive shaft and housed within the main pump housing.
  • the tubular member is provided with a plurality of apertures, each of which is shaped to guide reciprocal movement of an associated shoe as the roller rides over the cam surface.
  • the shoe associated with each plunger is of rectangular or square cross section.
  • a fuel pump assembly for use in an engine, the fuel pump assembly comprising a plurality of pump heads mounted upon a main pump housing, each of the pump heads including a pumping plunger which is reciprocable, in use, within a plunger bore under the influence of an associated drive arrangement so as to cause pressurisation of fuel within a pumping chamber defined within a pump head housing, the drive arrangement including a shoe and a roller which is cooperable with a driven cam, common to each of the pump heads, so as to impart reciprocal movement to the shoe as the cam is driven, in use, the shoe being of square or rectangular cross section and each pump head further comprising an associated insert, being formed as a separate part from the main pump housing but being assembled permanently therewith, wherein the insert defines a guide path of substantially rectangular or square cross section for guiding reciprocating movement of the associated shoe.
  • the invention provides the advantage that the insert of each pump head which defines the shoe guide path can be more accurately formed as a separate component, prior to it being fixed permanently to the main pump housing.
  • the problem encountered in known roller-shoe pump designs, that the accurate forming of a rectangular section guide path for the shoe is difficult to achieve, is therefore overcome by the present invention. As a result of being able to machine the shoe guide part with improved accuracy, wear on the guide path and the shoe is reduced.
  • the insert of each pump head has an external surface profile of substantially cylindrical form.
  • each of the inserts is preferably shaped to include two pairs of substantially parallel facing walls or internal surfaces (e.g. of substantially square or rectangular cross-sectional form).
  • the insert associated with each pump head housing is formed by sintering or metal injection moulding (MIM).
  • MIM metal injection moulding
  • said main pump housing is provided with a plurality of openings in the form of radially extending bores in the main pump housing, each of the bores being adapted to receive one of the inserts having an outer surface of cylindrical form.
  • the cylindrical insert of each pump head is an interference fit with the corresponding radially extending opening.
  • the insert is formed as a separate part from the main pump housing, when assembled within the housing it forms a permanent and immovable feature of the pump assembly. It is because the insert can be formed as a separate part, however, that their pairs of parallel facing walls can be formed conveniently, and with improved accuracy, compared with pump designs in which a main housing itself defines the guide path for the shoe.
  • Each pump head may be provided with a return spring which acts on the shoe so as to ensure the roller remains in engagement with the cam surface during a return stroke of the pumping plunger.
  • the roller may preferably take the form of a cylindrical roller.
  • the pump head housing has an integral plunger bore in the form of a plunger support tube extending substantially perpendicularly from the lower surface of the pump head housing so as to be located within the shoe guide path.
  • a first end of the return spring in the region of the pump head housing, surrounds the plunger support tube so as to retain the return spring in position.
  • a second end of the return spring distal to the pump head housing, is associated with positioning means to maintain the return spring in a fixed relationship with the shoe.
  • the positioning means includes an annular groove on the radially outer surface of the shoe.
  • the positioning means further includes a spring seat located on the inner end of the plunger, wherein the spring seat abuts the radially outer shoe surface.
  • each pump head is shaped to define, together with the opening in the main pump housing, a vent means for permitting fuel displaced by the shoe during reciprocating motion thereof to vent to low pressure.
  • the outer surface of each insert may be provided with at least one groove or recess which defines, together with the internal surface of the opening, a return flow path for fuel.
  • the fuel volume radially inward of the shoe can escape relatively easily between the main bore, through drillings in the main pump housing and through the recesses or grooves formed in the external surface of the insert, which define the return flow path.
  • the return flow path presents a relatively large flow area to fuel displaced by reciprocating motion of the shoes to ensure movement of the shoes is substantially unimpeded.
  • the fuel pump assembly has a pair of pump heads radially mounted upon the main pump housing at diametrically opposed positions about the drive shaft, and wherein the cam has a cam surface with a single cam lobe so as to impart phased, alternate motion to the respective plungers of the pair upon rotation of the shaft.
  • the fuel pump assembly has three pump heads, and thus three associated inserts to define the shoe guide paths, the pump heads being radially mounted upon the may pump housing at equi-angularly spaced locations about a pump drive shaft.
  • fuel pump assembly for use in an engine, the fuel pump assembly comprising at least one pair of pump heads mounted upon a main pump housing, each of the pump heads including a pumping plunger which is reciprocable, in use, within a plunger bore under the influence of an associated drive arrangement so as to cause pressurisation of fuel within a pumping chamber defined within a pump head housing, each of the drive arrangements being co-operable with a surface of a cam which is driven, in use, by an associated engine drive shaft, so as to impart reciprocal movement to the pumping plunger upon rotation of the drive shaft, wherein the cam surface is common to each of the pump heads and wherein one pump head of the or each pair is positioned at substantially 90° to the other pump head of the pair, the cam surface being shaped to result in there being two pressurisation events for each pump head of said pair per cycle as the drive shaft rotates.
  • only a single pair of pump heads are provided on the fuel pump assembly.
  • the cam is a twin lobed cam. More preferably the cam lobes are diametrically opposed.
  • each drive arrangement is a shoe and roller arrangement, or alternatively a slipper and tappet arrangement. It will be appreciated that, although it may be advantageous to provide the pump heads of the second aspect of the invention with an insert for guiding movement of the associated shoe, this is not essential.
  • a high pressure fuel pump assembly suitable for use in the fuel injection system of a compression ignition internal combustion engine.
  • the fuel pump assembly is suitable for use in delivering high pressure fuel to the common rail of a common rail fuel injection system.
  • the pump assembly includes a main pump housing 10 through which a cam drive shaft 12 of the engine extends along a drive shaft axis extending perpendicularly to the plane of the page.
  • a front housing plate 11 is positioned on the main pump housing 10 and located by means of a boss 11 a.
  • First, second and third pump heads 13a, 13b, 13c respectively are mounted upon the main pump housing 10 at approximately equi-angularly spaced radial locations around the drive shaft axis.
  • the drive shaft 12 extends through a central through bore 40 provided in the main pump housing 10, and is supported by a plain bearing bush 41 and a front plate bearing 41a.
  • Each pump head 13a, 13b, 13c includes a respective pump head housing 18a, 18b, 18c.
  • a seal member 72 in the form of a gasket is located in a recess between the main pump housing 10 and the pump head housing 18a, 18b, 18c so as to form a fluid tight seal between these parts when the pump heads 13a, 13b, 13c are secured to the housing 10 by means if screws 92.
  • the gasket seal 72 serves to seal low pressure regions of the pump from the high pressure regions of the pump, as discussed further below.
  • the first pump head 13a includes a pumping plunger 14 which is reciprocal within a blind bore 16 to perform a pumping cycle having a pumping stroke (or forward stroke) and a return stroke.
  • the blind bore 16 is defined partly within a pump head housing 18a and partly within a plunger support tube 20 which extends from a lower surface of the pump head housing 18a.
  • the bore 16 defines, at its blind end within the pump head housing 18a, a pumping chamber 22.
  • Reciprocating movement of the plunger 14 within the bore 16 causes pressurisation of fuel within the pumping chamber 22 during the pumping stroke.
  • the pumping plunger 14 is driven axially within the bore 16, in use, under the influence of a drive arrangement including a shoe 24 and an associated roller 26.
  • the shoe is a component having a substantially rectangular cross section, although square section shoes may also be used.
  • the roller 26 is co-operable with a cam surface 27 of a cam member 28 which is carried by the drive shaft 12. As the shaft 12 rotates in use, the roller 26 rides over the cam surface, imparting movement to the shoe 24 and, hence, imparting axial movement (i.e. along the main plunger axis) to the pumping plunger 14 within the bore 16 to drive the pumping stroke.
  • each pump head 13a, 13b, 13c co-operates with the cam surface 27, which is thus common to all three pump heads.
  • the rollers co-operate with the common cam surface 27 to cause reciprocating motion of the shoes in a phased, cyclic manner depending on the cam surface profile.
  • a radially extending opening 32 in the form of a radially extending bore is provided in the main pump housing 10.
  • the opening 32 defines an internal surface of substantially cylindrical form, and a first, hollow insert 30a, which is associated with the first pump head 13a, is located within the cylindrical opening 32 so as to be coaxial with the bore 16.
  • the insert 30a has an outer surface of substantially cylindrical form, which corresponds to the shaping of the internal surface of the opening 32 in the main pump housing 10.
  • the internal surface of the insert 30a defines a substantially rectangular cross section (in a plane perpendicular to the axis of movement of the plunger 14 and the shoe 24).
  • the internal surface of the insert 30a therefore defines first and second pairs of substantially parallel facing walls 34, 36, which define a guide path of appropriate form for the rectangular section shoe 24 as it reciprocates, in use.
  • the facing internal surfaces 34 of the first pair have a smaller length, along an axis perpendicular to the plunger axis, than the facing internal surfaces 36 of the second pair.
  • the insert 30a is also formed so that the first pair of internal surfaces 34 have a longer length, along the direction of the plunger axis, than the second pair of internal surfaces 36, and thus upper end regions 130 of the insert 30a are of increased axial height.
  • cross section of the insert guide path is not exactly rectangular (e.g. due to interconnecting corner regions 230 being of curved form - as shown in Figure 4), a guide path of substantially rectangular cross section is defined to provide an adequate guiding surface for the generally rectangular cross section of the shoe 24.
  • the second and third pump heads 13b, 13c are also provided with similar inserts 30b, 30c, respectively, each of the inserts 30b, 30c being received within a correspondingly shaped radial opening or bore (such as 32) in the main pump housing 10.
  • Each of first, second and third inserts 30a, 30b, 30c is arranged such that a radially inner end thereof opens into a main axial bore 38 provided in the main pump housing 10 (as can be seen in Figure 3).
  • the insert 30a also defines a spring space 74 located above the shoe 24 (in the orientation shown), within which a return spring 84 is located.
  • the return spring 84 serves to urge the shoe 24 and the roller 26 in a radially inward direction such that the roller 26 maintains contact with the cam surface 27 throughout a complete rotation of the drive shaft 12.
  • the force due to the return spring 84 is aided by the force due to fuel pressure within the pumping chamber 22 which acts on the pumping plunger 14 to provide a return force which serves to urge the pumping plunger 14 outwardly from the bore 16 to perform the return stroke. It will be appreciated that this only occurs if the pump is operating at its maximum displacement and, hence, at maximum filling.
  • the outer surface of the insert 30a is provided with first and second recesses 82a, 82b.
  • the recesses 82a, 82b are provided along those facing sides of the insert 30a which define the longer of the facing internal wall surfaces 36.
  • the recesses 82a, 82b are thus formed in the region of the insert 30a which would otherwise be formed from the greatest amount of insert material.
  • a plurality of drillings 80 are provided in the main pump housing 10 which, together with the recesses 82a, 82b provided in the outer surface of the insert 30a, define a vent passage means in the form of a return flow path, as discussed further below.
  • the return spring 84 is of a diameter such that a first end is located around, and retained in position by, the plunger support tube 20.
  • the second end of the return spring 84 abuts a spring seat 86 attached to the pumping plunger 14 by a retention clip 88.
  • the clip 88 acts to maintain the spring seat 86 in position.
  • the spring seat 86 is located in and spaced from an annular groove 90 provided on the radially outer surface of the shoe 24.
  • a low pressure transfer pump 42 is mounted upon the housing 10 at an end face remote from the front plate 11.
  • the transfer pump 42 is arranged to supply fuel at a pressure dependent upon the speed of rotation of the engine, the rate of flow of fuel from the transfer pump being controlled by means of a metering valve arrangement 44 in a conventional manner
  • the transfer pump 42 also supplies fuel at a low pressure to the main bore 38 and the spring space 74 through a drilling 76 in the main housing 10.
  • a back leak connector 45 is mounrted upon the front plate 11 in a conventional manner for use in the return of fuel from the pump assembly to a low pressure fuel reservoir (not shown).
  • the gasket seal 72 is a generally square frame seal having a side-tab seal portion 72b.
  • the metered flow of fuel from the transfer pump 42 is supplied to an entry drilling 55 provided in the pump head housing 18a, which extends through an aperture 72a in the side tab portion 72b of the gasket seal 72.
  • the entry drilling 55 communicates with the pump chamber 22 through an inlet valve arrangement 46, and thus defines a flow path for relatively low pressure fuel into the pumping chamber 22.
  • the upper end region 130 of the insert 30a defines a support or abutment for the gasket seal 72, which aids unwanted movement of the seal 72 relative to the housing surface 10, and thus benefits the gasket sealing function.
  • the inlet valve arrangement 46 includes a disc-like valve member 58 which is operable in response to fuel pressure within a further drilling 64 so as to control the flow of fuel into the pumping chamber 22 from the drillings 55, 64.
  • the further drilling 64 is defined within an inlet valve body 59 and communicates with an outlet end of the entry drilling 55.
  • the inlet valve body 59 is sealed within a bore in the pump head housing 18a by means of an O-ring 57 and a deformable knife-edge seal 60.
  • valve member 58 is biased closed by means of a first valve spring 56 and, if fuel pressure within the further drilling 64 exceeds a predetermined amount, the valve member 58 is caused to lift away from its seating, against the force of the spring 56, to permit a metered flow of fuel (at "metered fuel pressure") to be suppplied through the further drilling 64 to the pumping chamber 22.
  • the pumping chamber 22 is also provided with an outlet valve arrangement 48 which is arranged to open when fuel pressure within the pumping chamber 22 is pressurised to a level greater than a predetermined amount.
  • the outlet valve arrangement 48 takes the form of a ball valve including a ball 66 which is urged against a valve seating 67 by means of fuel pressure in the high pressure drillings.
  • the ball valve controls communication between the pumping chamber 22 and a common delivery passage 50.
  • a high pressure sealing member 70 is located between the outlet valve 48 and the common delivery passage 50.
  • the sealing member 70 may be a metal sealing washer of double knife-edged form which is trapped in an annular recess in the main pump housing 10.
  • the high pressure sealing member 70 has first and second so called 'knife-edge" sealing faces to ensure substantially no high pressure fuel leaks from the common delivery passage 50.
  • the common delivery passage 50 is defined within the main housing 10 and is common to all three of the pump heads 13a, 13b, 13c.
  • the common delivery passage 50 includes first, second and third radially extending arms 50a, 50b, 50c which define a flow passage of generally 'Y' shaped configuration such that stress concentration between the arms is minimised.
  • Fuel is delivered through the first one of the arms 50a to a common outlet port 52, through which high pressure fuel is delivered to the downstream parts of the fuel injection system, for example a common rail.
  • the high pressure delivery passage 50 also communicates with a high pressure limiting valve assembly 54 which acts to control the fuel pressure level within the housing 10.
  • metered fuel is delivered from the transfer pump 42 to the further drilling 64. If inlet fuel pressure exceeds an amount which is sufficient to overcome the force due to the first valve spring 56 and any pressure in the pumping chamber 22, the valve member 58 will be urged away from its seating to permit fuel flow into the pumping chamber 22.
  • the rollers 26 of each of the pump heads 13a, 13b, 13c are caused to move in a radially outward direction, thereby imparting movement to the associated shoe 24, such movement of the shoe 24 being guided by co-operation between the shoe and the walls 34, 36 of the insert 30a.
  • the pumping plunger 14 is caused to move axially within its bore 16 to pressurise fuel within the pumping chamber 22.
  • Fuel is also supplied by the transfer pump 42 to the pumping chambers of the second and third pump heads 13b, 13c such that, as the drive shaft 12 rotates and the respective rollers ride over the cam surface, the shoes reciprocate cyclically within their respective bores to pressurise fuel within the pumping chambers of the second and third pump heads 13b, 13c also.
  • the main pump housing 10 is filled with fuel at relatively low pressure (commonly referred to as "housing pressure” and generally controlled by a housing pressurising valve or an exit orifice) through a restricted feed (not shown) from the transfer pump 42.
  • Fuel pressure within this volume applies a force to the shoe 24, and hence to the associated pumping plunger 14, which serves to oppose outward movement of the pumping plunger 14 from the plunger bore 16.
  • Fuel passes between the main bore 38 and the spring space 74 through the drillings 80 in the main pump housing, and through the recesses 82a, 82b formed in the external surface of the insert 30a.
  • the drillings 80 and the recesses 82a, 82b define a return flow path for fuel displaced by the shoe 24 between the spring space 74 and the main axial bore 38, from where fuel flows to the low pressure return 45.
  • the return flow path presents a relatively large flow area to fuel displaced by reciprocating motion of the shoes to ensure movement of the shoes 24 is substantially unimpeded, and thus fuel pressure in the space 74 remains similar to that in the main bore 38.
  • the spring seat 86 for the return spring 84 and the retention clip 88 are removed, such that the return spring 84 acts directly on the shoe 24.
  • pressure in the space 74 acts on the exposed end of the plunger 14, and thus opposes to some extent (but does not prevent altogether) the entry of fuel into the pumping chamber 22.
  • the plunger 14 is maintained in contact with fuel entering the chamber 22 during the filling stroke, and the formation of vends or air bubbles in the filling circuit is prevented. In this case, a reduced pressure difference is necessary to open the valve 58.
  • One advantage of the present invention is that the use of a separate insert 30a to define a shoe guide path having a rectangular or square cross section to correspond with that of the shoe can be produced more accurately and easily. Wear and manufacturing difficulties are therefore reduced compared to existing roller-shoe pump designs.
  • a further advantage of the present invention is that the shoe and roller arrangements 24, 26 may be assembled within each individual insert in the main pump housing 10 before the pump head housings 18a,18b, 18c are mounted upon the main pump housing 10. Thus, manufacturing difficulties in assembling the shoe and roller arrangement 24, 26 from inside the main pump housing 10 are avoided. As the pump assembly is of multi-part construction, access for machining precision is also greatly improved and the assembly is readily adaptable for different user requirements.
  • each of the pump heads 13a, 13b, 13c is assembled separately to include the respective pumping plunger 14, the inlet and outlet valve arrangements 46, 48, and the spring 84.
  • the insert 30a is introduced into the passage 32 in the main pump housing 10 and is secured thereto in such a manner that it forms an interference fit with the opening 32 in the main pump housing 10 to become a permanent feature of the housing 10 (i.e. assembled in a permanent manner within the housing 10).
  • the insert 30a may be formed conveniently by sintering or by means of metal injection moulding (MIM).
  • Each assembled pump head 13a, 13b, 13c may then be presented to the main pump housing 10, such that the pumping plunger 14 and the return spring 84 are positioned against the shoe and roller arrangement 24, 26 of each pump head with the spring seat 86 received in the annular groove 90.
  • the pump head housing 18a,18b, 18c is clamped against the main pump housing 10, to compress the return spring 84 and the seals 70, 72 between the pump head housing 18a, 18b, 18c and the main pump housing 10.
  • the screws 92 are tightened into the screw-threaded drillings in the main pump housing 10 to secure the pump head housings 18a, 18b, 18c directly to the main pump housing 10.
  • a pair of pump heads is mounted upon a main pump housing, with one pump head of each pair being mounted upon the drive shaft at substantially 90° to the other pump head of the pair.
  • the cam arrangement takes the form of a twin-lobed cam having two cam surfaces, shaped to result in there being two pressurisation events for each pump head of said pair per cycle as the drive shaft rotates.
  • the drive arrangement for the pump head pair may be a roller/shoe or a slipper/tappet and need not be mounted in inserts 30a, 30b but may be guided within a guide path defined by the respective pump head housing 18a, 18b.
  • a pair of pump heads is mounted on the main housing diametrically opposite one another, such that rotation of the drive shaft and the associated cam results in the plungers pumping in an alternate, phased manner.
  • the plunger of the other pump head is at substantially the bottom of its stroke. It is envisaged that such an embodiment would be suitable for use in applications requiring a reduced rate of fuel delivery to the common rail.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP03256728A 2002-10-25 2003-10-24 Assemblage de pompe à essence Expired - Lifetime EP1413749B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0224936 2002-10-25
GBGB0224936.5A GB0224936D0 (en) 2002-10-25 2002-10-25 Fuel pump assembly

Publications (3)

Publication Number Publication Date
EP1413749A2 true EP1413749A2 (fr) 2004-04-28
EP1413749A3 EP1413749A3 (fr) 2004-10-27
EP1413749B1 EP1413749B1 (fr) 2005-08-17

Family

ID=9946633

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03256728A Expired - Lifetime EP1413749B1 (fr) 2002-10-25 2003-10-24 Assemblage de pompe à essence

Country Status (4)

Country Link
EP (1) EP1413749B1 (fr)
AT (1) ATE302343T1 (fr)
DE (1) DE60301312T2 (fr)
GB (1) GB0224936D0 (fr)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2400418A (en) * 2003-04-08 2004-10-13 Delphi Tech Inc Liner for a pump assembly
WO2005088125A1 (fr) * 2004-03-09 2005-09-22 Robert Bosch Gmbh Pompe haute pression, notamment pour un dispositif d'injection de carburant d'un moteur a combustion interne
DE102004048711A1 (de) * 2004-10-06 2006-04-13 Siemens Ag Radialkolbenpumpe mit Rollenstößel
WO2006072277A1 (fr) * 2004-12-23 2006-07-13 Alfred Kärcher Gmbh & Co. Kg Tete de nettoyage a pompe a pistons radiaux et appareil de nettoyage de surfaces pourvu d'une tete de nettoyage de ce type
WO2007096224A1 (fr) * 2006-02-20 2007-08-30 Robert Bosch Gmbh Pompe haute pression conçue en particulier pour un dispositif d'injection de carburant d'un moteur à combustion interne
WO2009098095A1 (fr) * 2008-02-04 2009-08-13 Robert Bosch Gmbh Came sans effort transversal pour pompes haute pression à rampe commune
ITMI20081470A1 (it) * 2008-08-05 2010-02-06 Bosch Gmbh Robert Pompa di alta pressione per alimentare combustibile a un motore a combustione interna
WO2010094573A1 (fr) * 2009-02-18 2010-08-26 Robert Bosch Gmbh Pompe d'alimentation en carburant haute pression à réservoir haute pression intégré
US7793867B2 (en) 2005-02-08 2010-09-14 Continential Automotive Gmbh Method for producing an injector body and corresponding injector body
WO2010118903A1 (fr) * 2009-04-16 2010-10-21 Robert Bosch Gmbh Pompe à piston avec entraînement par came, en particulier pompe à carburant
DE102013101121A1 (de) 2012-02-10 2013-08-14 Denso Corporation Kraftstoffversorgungspumpe
GB2522204A (en) * 2014-01-15 2015-07-22 Newlenoir Ltd Piston arrangement
GB2555595A (en) * 2016-11-02 2018-05-09 Delphi Int Operations Luxembourg Sarl Fuel pump and shoe guide
CN115638094A (zh) * 2022-11-03 2023-01-24 山东泰展机电科技股份有限公司 凸轮式空气泵

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1206453A (en) * 1911-07-19 1916-11-28 Charles Matthews Manly Variable-speed power-transmitting mechanism.
EP0517991A1 (fr) * 1991-06-12 1992-12-16 Tiby M. Martin Rampe à injection de combustible électronique de haute pression pour moteurs diesel
US5752430A (en) * 1996-07-16 1998-05-19 Denso Corporation High pressure fuel supply pump for engine
EP1013921A2 (fr) * 1998-12-25 2000-06-28 Denso Corporation Pompe d'injection de carburant
DE19907311A1 (de) * 1999-02-22 2000-08-31 Bosch Gmbh Robert Hydraulikpumpeneinheit
EP1223334A2 (fr) * 2001-01-10 2002-07-17 Delphi Technologies, Inc. Pompe à carburant

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1206453A (en) * 1911-07-19 1916-11-28 Charles Matthews Manly Variable-speed power-transmitting mechanism.
EP0517991A1 (fr) * 1991-06-12 1992-12-16 Tiby M. Martin Rampe à injection de combustible électronique de haute pression pour moteurs diesel
US5752430A (en) * 1996-07-16 1998-05-19 Denso Corporation High pressure fuel supply pump for engine
EP1013921A2 (fr) * 1998-12-25 2000-06-28 Denso Corporation Pompe d'injection de carburant
DE19907311A1 (de) * 1999-02-22 2000-08-31 Bosch Gmbh Robert Hydraulikpumpeneinheit
EP1223334A2 (fr) * 2001-01-10 2002-07-17 Delphi Technologies, Inc. Pompe à carburant

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2400418A (en) * 2003-04-08 2004-10-13 Delphi Tech Inc Liner for a pump assembly
WO2005088125A1 (fr) * 2004-03-09 2005-09-22 Robert Bosch Gmbh Pompe haute pression, notamment pour un dispositif d'injection de carburant d'un moteur a combustion interne
US7762176B2 (en) 2004-10-06 2010-07-27 Continental Automotive Gmbh Radial piston pump with a roller plunger
DE102004048711A1 (de) * 2004-10-06 2006-04-13 Siemens Ag Radialkolbenpumpe mit Rollenstößel
DE102004048711B4 (de) * 2004-10-06 2006-09-14 Siemens Ag Radialkolbenpumpe mit Rollenstößel
WO2006072277A1 (fr) * 2004-12-23 2006-07-13 Alfred Kärcher Gmbh & Co. Kg Tete de nettoyage a pompe a pistons radiaux et appareil de nettoyage de surfaces pourvu d'une tete de nettoyage de ce type
US7600698B2 (en) 2004-12-23 2009-10-13 Alfred Kaercher Gmbh & Co. Kg Cleaning head and surface cleaning device comprising said type of cleaning head
US7793867B2 (en) 2005-02-08 2010-09-14 Continential Automotive Gmbh Method for producing an injector body and corresponding injector body
WO2007096224A1 (fr) * 2006-02-20 2007-08-30 Robert Bosch Gmbh Pompe haute pression conçue en particulier pour un dispositif d'injection de carburant d'un moteur à combustion interne
US8191459B2 (en) 2006-02-20 2012-06-05 Robert Bosch Gmbh High pressure pump, in particular for a fuel injection system of an internal combustion engine
WO2009098095A1 (fr) * 2008-02-04 2009-08-13 Robert Bosch Gmbh Came sans effort transversal pour pompes haute pression à rampe commune
WO2010015448A1 (fr) * 2008-08-05 2010-02-11 Robert Bosch Gmbh Pompe haute pression pour alimenter un moteur à combustion interne en carburant
ITMI20081470A1 (it) * 2008-08-05 2010-02-06 Bosch Gmbh Robert Pompa di alta pressione per alimentare combustibile a un motore a combustione interna
WO2010094573A1 (fr) * 2009-02-18 2010-08-26 Robert Bosch Gmbh Pompe d'alimentation en carburant haute pression à réservoir haute pression intégré
CN102395788A (zh) * 2009-04-16 2012-03-28 罗伯特·博世有限公司 具有凸轮驱动装置的活塞泵、尤其是燃料泵
CN102395788B (zh) * 2009-04-16 2014-10-29 罗伯特·博世有限公司 具有凸轮驱动装置的活塞泵、尤其是燃料泵
WO2010118903A1 (fr) * 2009-04-16 2010-10-21 Robert Bosch Gmbh Pompe à piston avec entraînement par came, en particulier pompe à carburant
DE102013101121B4 (de) * 2012-02-10 2016-02-18 Denso Corporation Kraftstoffversorgungspumpe mit einem Lagerelement für einen Rollenstößel
DE102013101121A1 (de) 2012-02-10 2013-08-14 Denso Corporation Kraftstoffversorgungspumpe
US8915232B2 (en) 2012-02-10 2014-12-23 Denso Corporation Fuel supply pump
GB2522204B (en) * 2014-01-15 2016-06-22 Newlenoir Ltd Piston arrangement
GB2522204A (en) * 2014-01-15 2015-07-22 Newlenoir Ltd Piston arrangement
US10472964B2 (en) 2014-01-15 2019-11-12 Newlenoir Limited Piston arrangement
US10858938B2 (en) 2014-01-15 2020-12-08 Newlenoir Limited Piston arrangement
US11008863B2 (en) 2014-01-15 2021-05-18 Newlenoir Limited Piston arrangement
GB2555595A (en) * 2016-11-02 2018-05-09 Delphi Int Operations Luxembourg Sarl Fuel pump and shoe guide
EP3318746A1 (fr) * 2016-11-02 2018-05-09 Delphi International Operations Luxembourg S.à r.l. Pompe à carburant et guide chaussure
CN115638094A (zh) * 2022-11-03 2023-01-24 山东泰展机电科技股份有限公司 凸轮式空气泵
CN115638094B (zh) * 2022-11-03 2023-08-25 山东泰展机电科技股份有限公司 凸轮式空气泵

Also Published As

Publication number Publication date
EP1413749A3 (fr) 2004-10-27
DE60301312T2 (de) 2006-05-18
DE60301312D1 (de) 2005-09-22
EP1413749B1 (fr) 2005-08-17
GB0224936D0 (en) 2002-12-04
ATE302343T1 (de) 2005-09-15

Similar Documents

Publication Publication Date Title
EP1413749B1 (fr) Assemblage de pompe à essence
EP1629191B1 (fr) Ensemble de pompe
US8070462B2 (en) High-pressure fuel pump
JP5187255B2 (ja) 高圧ポンプ
JP5187254B2 (ja) 高圧ポンプ
EP2063093A1 (fr) Système d'injection de carburant
EP1184568B1 (fr) Pompe à carburant
JP4589382B2 (ja) 内燃機関の燃料噴射装置用の高圧ポンプ
US8215925B2 (en) Pump assembly and tappet therefor
KR0167112B1 (ko) 내연기관용 연료 분배식 분사 펌프
CN1112370A (zh) 内燃机燃油喷射装置
JP3823819B2 (ja) 燃料噴射ポンプ
JPH09256955A (ja) ベローズ式燃料ポンプ
US4842496A (en) Fuel injection pump for internal combustion engines including onset of supply control means
EP1363016A2 (fr) Pompe à carburant
EP1489301B1 (fr) Système d'entraînement pour une Pompe
EP1431577B1 (fr) Pompe à carburant
JP2017101621A (ja) リリーフ弁装置、及び、それを用いる高圧ポンプ
GB2588752A (en) Fuel pump assembly
EP2184491A1 (fr) Tête de pompe pour ensemble de pompe à carburant
JPH0331580A (ja) ラジアルプランジャポンプ
EP0372713B1 (fr) Pompe d'injection de combustible
GB2384529A (en) Fuel pump assembly
EP1223334A2 (fr) Pompe à carburant
EP1336752A2 (fr) Système d'injection de carburant

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

17P Request for examination filed

Effective date: 20050125

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

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

Ref country code: RO

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

Effective date: 20050817

Ref country code: EE

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

Effective date: 20050817

Ref country code: CH

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

Effective date: 20050817

Ref country code: SI

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

Effective date: 20050817

Ref country code: NL

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

Effective date: 20050817

Ref country code: AT

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

Effective date: 20050817

Ref country code: FI

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

Effective date: 20050817

Ref country code: LI

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

Effective date: 20050817

Ref country code: BE

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

Effective date: 20050817

Ref country code: TR

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

Effective date: 20050817

Ref country code: SK

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

Effective date: 20050817

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 60301312

Country of ref document: DE

Date of ref document: 20050922

Kind code of ref document: P

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

Ref country code: CY

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

Effective date: 20051024

Ref country code: IE

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

Effective date: 20051024

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

Ref country code: MC

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

Effective date: 20051031

Ref country code: LU

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

Effective date: 20051031

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

Ref country code: SE

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

Effective date: 20051117

Ref country code: GR

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

Effective date: 20051117

Ref country code: DK

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

Effective date: 20051117

Ref country code: BG

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

Effective date: 20051117

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

Ref country code: ES

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

Effective date: 20051128

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

Ref country code: PT

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

Effective date: 20060117

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

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

Effective date: 20060218

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20060518

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20130425 AND 20130501

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20140220 AND 20140226

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

Owner name: DELPHI INTERNATIONAL OPERATIONS LUXEMBOURG S.A, LU

Effective date: 20140516

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 60301312

Country of ref document: DE

Representative=s name: MANITZ, FINSTERWALD & PARTNER GBR, DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 60301312

Country of ref document: DE

Representative=s name: MANITZ, FINSTERWALD & PARTNER GBR, DE

Effective date: 20140702

Ref country code: DE

Ref legal event code: R081

Ref document number: 60301312

Country of ref document: DE

Owner name: DELPHI INTERNATIONAL OPERATIONS LUXEMBOURG S.A, LU

Free format text: FORMER OWNER: DELPHI TECHNOLOGIES HOLDING S.A.R.L., BASCHARAGE, LU

Effective date: 20140702

Ref country code: DE

Ref legal event code: R082

Ref document number: 60301312

Country of ref document: DE

Representative=s name: MANITZ FINSTERWALD PATENTANWAELTE PARTMBB, DE

Effective date: 20140702

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 15

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 16

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 60301312

Country of ref document: DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 60301312

Country of ref document: DE

Owner name: DELPHI TECHNOLOGIES IP LIMITED, BB

Free format text: FORMER OWNER: DELPHI INTERNATIONAL OPERATIONS LUXEMBOURG S.A R.L., BASCHARAGE, LU

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20190222 AND 20190227

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

Ref country code: GB

Payment date: 20220914

Year of fee payment: 20

Ref country code: CZ

Payment date: 20220920

Year of fee payment: 20

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

Ref country code: FR

Payment date: 20220916

Year of fee payment: 20

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

Ref country code: IT

Payment date: 20221014

Year of fee payment: 20

Ref country code: DE

Payment date: 20220914

Year of fee payment: 20

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230327

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 60301312

Country of ref document: DE

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20231023

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

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20231023

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

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20231023

Ref country code: CZ

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20231024

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 60301312

Country of ref document: DE

Owner name: PHINIA DELPHI LUXEMBOURG SARL, LU

Free format text: FORMER OWNER: DELPHI TECHNOLOGIES IP LIMITED, ST. MICHAEL, BB