EP3402979B1 - Fuel pump - Google Patents
Fuel pump Download PDFInfo
- Publication number
- EP3402979B1 EP3402979B1 EP17700137.7A EP17700137A EP3402979B1 EP 3402979 B1 EP3402979 B1 EP 3402979B1 EP 17700137 A EP17700137 A EP 17700137A EP 3402979 B1 EP3402979 B1 EP 3402979B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- plunger
- engagement
- spring seat
- central
- aperture
- 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 17
- 238000005086 pumping Methods 0.000 claims description 20
- 230000002093 peripheral effect Effects 0.000 claims description 11
- 230000000717 retained effect Effects 0.000 claims description 2
- 210000003414 extremity Anatomy 0.000 description 16
- 238000002485 combustion reaction Methods 0.000 description 3
- 238000003754 machining Methods 0.000 description 3
- 230000000295 complement effect Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000004806 packaging method and process Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 210000001364 upper extremity Anatomy 0.000 description 1
Images
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
- F02M59/44—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
- F02M59/48—Assembling; Disassembling; Replacing
-
- 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
- F02M59/44—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
-
- 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
Definitions
- the present invention relates to a cam actuated high pressure fuel pump adapted to be arranged in a fuel injection equipment of an internal combustion engine.
- the invention particularly focuses on the arrangement of a spring seat onto the extremity of a plunger.
- Fuel injection equipment comprise high pressure pump aiming at pressurizing fuel at several thousands of bars prior to flow said fuel to injectors that spray the fuel in combustion chambers of an internal combustion engine.
- a known high pressure fuel pump comprises a pumping head provided with a bore in which a piston translates along a pumping axis of the bore performing a pumping cycle.
- the piston also identified as a plunger, performs the pumping cycle between a Top Dead Centre (TDC) position around which fuel in the compression chamber is compressed and, a Bottom Dead Centre (BDC) position around which fuel is aspired in the chamber.
- TDC Top Dead Centre
- BDC Bottom Dead Centre
- the piston reciprocates under the influence of a cam rotating about a cam axis perpendicular to the pumping axis.
- the cam is followed by a cam follower combined to an external extremity of the piston, said cam follower typically having a cup-like body member in which a roller is free to rotate about a rolling axis perpendicular to the piston axis and parallel to the cam axis.
- a spring arranged around the plunger and compressed between the pumping head and a spring seat cooperating with the cam follower and fixed to the extremity of the plunger maintains the roller in contact against the outer track of the cam.
- the spring permanently bias the cam follower against the cam and it also pulls the piston as it travels from the Top Dead Centre (TDC) position to the Bottom Dead Centre (BDC) position thanks to the engagement of the spring seat member and the plunger.
- the spring seat is an axisymmetric part having a central circular portion, for complementary arrangement to the extremity of the plunger, a perpendicular cylindrical portion axially extending from the circular edge of the central portion and, a peripheral annular disc portion for receiving the spring.
- the central and peripheral portions extend in parallel plans separated from each other by the cylindrical portion.
- the spring seat is mounted to an outer diameter of the piston by pressing.
- the spring seat member may be fixedly mounted to the piston such that relative movement is inhibited.
- a mounting collar may be fixedly mounted to an outer diameter of the piston to support the spring seat member, for example by press fitting.
- the spring seat member may be movable relative to the piston, but is operatively biased against the collar by the action of the spring.
- the spring seat and the collar may both be press-fitted on the plunger.
- a further alternative is to form a keyed interface for mounting the spring seat member to the piston.
- the keyed interface may not require a press fit arrangement, but machining is required to form the keyed interface on the piston and/or the spring seat member.
- the spring seat comprises a central portion surrounded with a peripheral disc portion for receiving the spring, the central portion being provided with a central aperture allowing the plunger to pass therethrough and be positioned in a final position.
- the spring seat further comprises an engagement aperture enabling through engagement of the extremity of the plunger in a preliminary engagement position distinct from the final position, said engagement aperture opening into the central aperture so that the plunger can be moved from the engagement position to the final position.
- the extremity of the plunger is provided with a transverse diametral through hole in which is engaged a pin protruding from both extremities of the hole, the engagement aperture enabling passage of said pin until final positioning of the plunger in the central aperture.
- the engagement aperture has a rectangular section forming diametrally opposed slots radially extending from the circular central aperture so that the plunger and the pin can be engaged therethrough said central and engagement apertures prior to be rotated to the final position.
- the spring seat is further provided with rectangular notches forming recess in the central portion of the spring seat, the notches radially extending from the circular central opening, so that the pin can position in said notches when the plunger is in final position.
- the final position is 90° apart from the engagement position.
- the spring seat may comprise a cylindrical portion axially extending from a first circular edge to an opposed second circular edge, the central portion wherein is arranged the central opening inwardly radially extending from the first circular edge and, the peripheral disc portion for receiving the spring outwardly radially extending from the second circular edge.
- the engagement aperture partially opens in the wall of said cylindrical portion.
- a high pressure fuel pump 10 having a pumping head 12 wherein fuel at low pressure enters via an inlet into a compression chamber wherefrom it is expelled pressurized via an outlet, after a cylindrical piston 14, having diameter D14, reciprocally translating in a bore 16 along a pumping axis X has performed a pumping cycle.
- the piston 14 protrudes outside the pumping head 12 and extends toward an external extremity 18 where is arranged a spring seat 20 cooperating with a cam-follower 22 permanently maintained in contact against the outer track of a rotating cam 24 by a spring 26 that is compressed between a face of the pumping head 12 and the spring seat 20.
- the cam 24 rotates, the follower 22 imparts to the piston 14 a reciprocating movement generating said pumping cycle.
- the piston 14 is described having a constant diameter D14 throughout its length from the extremity inside the bore 16 to the external extremity.
- the external extremity of the plunger may have a slightly smaller diameter than the upper extremity that slides in the bore.
- the spring seat 20 comprises a central circular portion 28, a perpendicular cylindrical portion 30 axially extending from the peripheral circular edge of the central circular portion 28 to another distant circular edge and, a peripheral annular disc portion 32 outwardly extending from said another distant circular edge.
- the central 28 and the peripheral 32 portions extend in parallel plans transverse to the pumping axis X, and are separated from each other by the height of the cylindrical portion 30.
- the peripheral annular disc portion 32 is adapted to receive the spring 26. This defines an orientation of the spring seat 20 where an upper-side faces the pumping head, best shown on figure 4 , is opposed to an under-side facing the cam, best shown on figure 5 .
- the terms such as upper and under are only utilized to ease and clarify the description without any intent to limit the scope of the invention.
- the under-side has a concave shape, the cylindrical portion defining an under space S.
- the extremity 18 of the plunger is provided with a pin 36 fixedly arranged in a diametral through hole 38 pierced in said external extremity of the plunger.
- the pin 36 symmetrically protruding from both sides of the plunger is, in a preferred embodiment, an elastic pin enabling press engagement and fixation in the hole 38 via elastic contact pressure.
- Coiled pin, slotted elastic pin or solid cylindrical rod are also possible alternatives.
- the central portion 28 of the spring seat is provided with a circular central aperture 34 of diameter D34 slightly superior to the diameter D14 of the plunger. From said central aperture 34 radially extend two diametrally opposed lateral rectangular apertures 40 having dimensions slightly superior to the dimensions of the pin in order to enable through passage of the pin 36.
- the lateral rectangular apertures 40 are also identified as engagement aperture 34.
- the lateral rectangular extensions 40 extend within the central portion 28 of the spring seat and do not cut into the cylindrical portion 30.
- the lateral rectangular extensions 40 may extend to the cylindrical portion and cut out said lateral face of the spring seat.
- the pin 36 is firstly engaged in the hole 38 of the plunger so that said pin 36 symmetrically protrudes from both sides of the hole. Secondly, the plunger and pin assembly is placed before the spring seat oriented and axially aligned with the central aperture 34 and its lateral rectangular extensions 40 then, thirdly, the plunger and pin assembly is axially X engaged through the central portion of the spring seat, the plunger 14 passing through the central aperture 34 and the pin 36 passing through the lateral rectangular extensions 40. This intermediate position where the pin is aligned with the lateral apertures is identified as the engagement position.
- the plunger is rotated about the axis X by 90°, so that the pin 36 is no longer aligned with the lateral rectangular extensions 40. Said position where the spring seat cannot disengage from the shaft is identified as being the final position.
- the under-side of the central portion of the spring seat is provided with two lateral notches 42 diametrally opposed and radially extending from the central aperture 34. Said notches 42, arranged 90° apart from the lateral extensions 34, set the final position, the pin 36 being complementary arranged in the notches.
- the machining of the notches 42 is done radially from the outside of the spring seat so that round openings in the peripheral cylindrical face 30 are made and are visible.
- the machining of said notches 42 is entirely done via the underside of the spring seat without leaving openings in the cylindrical face.
- the angle between the engagement position and the final position of the spring seat is described as 90° but other angles are possible, provided said other angle is sufficient to keep the pin distant from the lateral extensions.
- the height of the space S is adjusted to the length of the extremity of the plunger protruding in the under-side of the central portion.
- Other arrangements where the plunger is slightly longer and extends below the spring seat or, to the contrary where the plunger is shorter are also possible.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Description
- The present invention relates to a cam actuated high pressure fuel pump adapted to be arranged in a fuel injection equipment of an internal combustion engine. The invention particularly focuses on the arrangement of a spring seat onto the extremity of a plunger.
- Fuel injection equipment comprise high pressure pump aiming at pressurizing fuel at several thousands of bars prior to flow said fuel to injectors that spray the fuel in combustion chambers of an internal combustion engine.
-
US2002/0085936 andDE2314596 are relevant prior art. A known high pressure fuel pump comprises a pumping head provided with a bore in which a piston translates along a pumping axis of the bore performing a pumping cycle. The piston, also identified as a plunger, performs the pumping cycle between a Top Dead Centre (TDC) position around which fuel in the compression chamber is compressed and, a Bottom Dead Centre (BDC) position around which fuel is aspired in the chamber. The piston reciprocates under the influence of a cam rotating about a cam axis perpendicular to the pumping axis. The cam is followed by a cam follower combined to an external extremity of the piston, said cam follower typically having a cup-like body member in which a roller is free to rotate about a rolling axis perpendicular to the piston axis and parallel to the cam axis. - A spring arranged around the plunger and compressed between the pumping head and a spring seat cooperating with the cam follower and fixed to the extremity of the plunger maintains the roller in contact against the outer track of the cam. The spring permanently bias the cam follower against the cam and it also pulls the piston as it travels from the Top Dead Centre (TDC) position to the Bottom Dead Centre (BDC) position thanks to the engagement of the spring seat member and the plunger.
- The spring seat is an axisymmetric part having a central circular portion, for complementary arrangement to the extremity of the plunger, a perpendicular cylindrical portion axially extending from the circular edge of the central portion and, a peripheral annular disc portion for receiving the spring. The central and peripheral portions extend in parallel plans separated from each other by the cylindrical portion.
- In known arrangements, the spring seat is mounted to an outer diameter of the piston by pressing. The spring seat member may be fixedly mounted to the piston such that relative movement is inhibited.
- Alternatively, a mounting collar may be fixedly mounted to an outer diameter of the piston to support the spring seat member, for example by press fitting. In this arrangement, the spring seat member may be movable relative to the piston, but is operatively biased against the collar by the action of the spring. Also, the spring seat and the collar may both be press-fitted on the plunger. Although this solves certain issues, for instance packaging issues, a problem with this type of arrangement is that the piston and seat member is not modular since to disassemble the spring seat, the collar needs to be disassembled first.
- A further alternative is to form a keyed interface for mounting the spring seat member to the piston. The keyed interface may not require a press fit arrangement, but machining is required to form the keyed interface on the piston and/or the spring seat member.
- These assemblies require high precision and costly manufacturing of both the plunger and the spring seat.
- Accordingly, it is an object of the present invention to resolve the above mentioned problems in providing a high pressure fuel pump wherein a spring engaged around a cylindrical plunger is compressed between a spring seat arranged and retained at an extremity of the plunger and a pumping head in which the plunger is slidably guided and arranged to perform a pumping cycle.
- More precisely, the spring seat comprises a central portion surrounded with a peripheral disc portion for receiving the spring, the central portion being provided with a central aperture allowing the plunger to pass therethrough and be positioned in a final position.
- The spring seat further comprises an engagement aperture enabling through engagement of the extremity of the plunger in a preliminary engagement position distinct from the final position, said engagement aperture opening into the central aperture so that the plunger can be moved from the engagement position to the final position.
- The extremity of the plunger is provided with a transverse diametral through hole in which is engaged a pin protruding from both extremities of the hole, the engagement aperture enabling passage of said pin until final positioning of the plunger in the central aperture.
- The engagement aperture has a rectangular section forming diametrally opposed slots radially extending from the circular central aperture so that the plunger and the pin can be engaged therethrough said central and engagement apertures prior to be rotated to the final position.
- The spring seat is further provided with rectangular notches forming recess in the central portion of the spring seat, the notches radially extending from the circular central opening, so that the pin can position in said notches when the plunger is in final position.
- In a preferred embodiment, the final position is 90° apart from the engagement position.
- More precisely, the spring seat may comprise a cylindrical portion axially extending from a first circular edge to an opposed second circular edge, the central portion wherein is arranged the central opening inwardly radially extending from the first circular edge and, the peripheral disc portion for receiving the spring outwardly radially extending from the second circular edge.
- In further embodiment, the engagement aperture partially opens in the wall of said cylindrical portion.
- The present invention is now described by way of example with reference to the accompanying drawings in which:
-
Figure 1 is an axial section of a high pressure pump as per the invention. -
Figure 2 is a magnified section of the pump offigure 1 particularly magnifying the invention comprising a plunger and spring seat arrangement. -
Figures 3 ,4 and 5 are isometric and bottom views of the invention. - In reference to
figure 1 is generally described a highpressure fuel pump 10 having a pumpinghead 12 wherein fuel at low pressure enters via an inlet into a compression chamber wherefrom it is expelled pressurized via an outlet, after acylindrical piston 14, having diameter D14, reciprocally translating in abore 16 along a pumping axis X has performed a pumping cycle. - Although the invention has first been thought for a diesel fuel pump where "low" pressure is in the range of few bars, less than ten and, "high" pressure ranges up to three thousand bars, the invention as described can be applied to gasoline pump, or even any type of cam actuated fluid pump.
- As it is known in the art, the
piston 14 protrudes outside the pumpinghead 12 and extends toward anexternal extremity 18 where is arranged aspring seat 20 cooperating with a cam-follower 22 permanently maintained in contact against the outer track of a rotatingcam 24 by aspring 26 that is compressed between a face of the pumpinghead 12 and thespring seat 20. As in use thecam 24 rotates, thefollower 22 imparts to the piston 14 a reciprocating movement generating said pumping cycle. - The
piston 14 is described having a constant diameter D14 throughout its length from the extremity inside thebore 16 to the external extremity. In alternative design the external extremity of the plunger may have a slightly smaller diameter than the upper extremity that slides in the bore. - More precisely, in reference to
figures 2 to 5 , thespring seat 20 comprises a centralcircular portion 28, a perpendicularcylindrical portion 30 axially extending from the peripheral circular edge of the centralcircular portion 28 to another distant circular edge and, a peripheralannular disc portion 32 outwardly extending from said another distant circular edge. The central 28 and the peripheral 32 portions extend in parallel plans transverse to the pumping axis X, and are separated from each other by the height of thecylindrical portion 30. While thecentral portion 28 is adapted to be arranged on the plunger, the peripheralannular disc portion 32 is adapted to receive thespring 26. This defines an orientation of thespring seat 20 where an upper-side faces the pumping head, best shown onfigure 4 , is opposed to an under-side facing the cam, best shown onfigure 5 . The terms such as upper and under are only utilized to ease and clarify the description without any intent to limit the scope of the invention. - As visible on the figures the under-side has a concave shape, the cylindrical portion defining an under space S.
- The
extremity 18 of the plunger is provided with apin 36 fixedly arranged in a diametral throughhole 38 pierced in said external extremity of the plunger. Thepin 36 symmetrically protruding from both sides of the plunger is, in a preferred embodiment, an elastic pin enabling press engagement and fixation in thehole 38 via elastic contact pressure. Coiled pin, slotted elastic pin or solid cylindrical rod are also possible alternatives. - The
central portion 28 of the spring seat is provided with a circularcentral aperture 34 of diameter D34 slightly superior to the diameter D14 of the plunger. From saidcentral aperture 34 radially extend two diametrally opposed lateralrectangular apertures 40 having dimensions slightly superior to the dimensions of the pin in order to enable through passage of thepin 36. The lateralrectangular apertures 40 are also identified asengagement aperture 34. - As shown in
figures 3 ,4 and 5 , in a preferred embodiment, the lateralrectangular extensions 40 extend within thecentral portion 28 of the spring seat and do not cut into thecylindrical portion 30. In a non-represented alternative the lateralrectangular extensions 40 may extend to the cylindrical portion and cut out said lateral face of the spring seat. Also, theextensions 40 and designated "rectangular" even if, as shown on the figures, the angles of said extensions are rounded. - For arranging this embodiment, the
pin 36 is firstly engaged in thehole 38 of the plunger so that saidpin 36 symmetrically protrudes from both sides of the hole. Secondly, the plunger and pin assembly is placed before the spring seat oriented and axially aligned with thecentral aperture 34 and its lateralrectangular extensions 40 then, thirdly, the plunger and pin assembly is axially X engaged through the central portion of the spring seat, theplunger 14 passing through thecentral aperture 34 and thepin 36 passing through the lateralrectangular extensions 40. This intermediate position where the pin is aligned with the lateral apertures is identified as the engagement position. Fourthly, once thepin 36 is in the under-side of the spring seat in said engagement position, the plunger is rotated about the axis X by 90°, so that thepin 36 is no longer aligned with the lateralrectangular extensions 40. Said position where the spring seat cannot disengage from the shaft is identified as being the final position. - Furthermore, in order to secure the final position of said plunger and pin assembly and to prevent later rotations that would re-align the
pin 36 with the lateralrectangular extensions 40 and enable dis-engagement of the spring seat, the under-side of the central portion of the spring seat is provided with twolateral notches 42 diametrally opposed and radially extending from thecentral aperture 34. Saidnotches 42, arranged 90° apart from thelateral extensions 34, set the final position, thepin 36 being complementary arranged in the notches. In the alternative shown onfigure 4 , the machining of thenotches 42 is done radially from the outside of the spring seat so that round openings in the peripheralcylindrical face 30 are made and are visible. In another alternative shown onfigure 3 , the machining of saidnotches 42 is entirely done via the underside of the spring seat without leaving openings in the cylindrical face. - The angle between the engagement position and the final position of the spring seat is described as 90° but other angles are possible, provided said other angle is sufficient to keep the pin distant from the lateral extensions.
- Also, as visible on
figure 2 , in the described embodiment the height of the space S is adjusted to the length of the extremity of the plunger protruding in the under-side of the central portion. Other arrangements where the plunger is slightly longer and extends below the spring seat or, to the contrary where the plunger is shorter are also possible. -
- X
- pumping axis
- 10
- pump
- 12
- pumping head
- 14
- piston - plunger
- 16
- bore
- 18
- extremity of the piston
- 20
- spring seat
- 22
- cam follower
- 24
- cam
- 26
- spring
- 28
- central portion of the spring seat
- 30
- cylindrical portion
- 32
- annular disc portion
- 34
- central aperture
- 36
- pin
- 38
- hole
- 40
- lateral rectangular extensions
- 42
- notches
- D14
- diameter of the plunger
- D34
- diameter of the central aperture
- S
- space
Claims (4)
- High pressure fuel pump (10) wherein a spring (26) engaged around a cylindrical plunger (14) is compressed between a spring seat (20) arranged and retained at an extremity (18) of the plunger and a pumping head (12) in which the plunger (14) is slidably guided and arranged to perform a pumping cycle,
the spring seat (20) comprising a central portion (28) surrounded by a peripheral disc portion (32) for receiving the spring (26), the central portion (28) being provided with a central aperture (34) allowing the plunger (14) to pass therethrough and be positioned in a final position,
characterized in that
the spring seat (20) further comprises a engagement aperture (34) enabling through engagement of the extremity (18) of the plunger in a preliminary engagement position distinct from the final position, said engagement aperture (34) opening into the central aperture (34) so that the plunger (14) can be moved from the engagement position to the final position and wherein,
the extremity (18) of the plunger is provided with a transverse diametral through hole (38) in which is engaged a pin (36) protruding from both extremities of the hole (38), the engagement aperture (34) enabling passage of said pin until final positioning of the plunger (14) in the central aperture (34) and,
wherein the engagement aperture (34) has a rectangular section forming diametrally opposed slots radially extending from the circular central aperture (34) so that the plunger (14) and the pin (36) can be engaged therethrough said central (34) and engagement (34) apertures prior to be rotated to the final position and,
wherein the spring seat (20) is further provided with rectangular notches (42) forming recess in the central portion (32) of the spring seat, the notches (42) radially extending from the circular central opening (34), so that the pin (36) can position in said notches (42) when the plunger is in final position. - High pressure fuel pump (10) as claimed the claim 1 wherein the final position is 90° apart from the engagement position.
- High pressure fuel pump (10) as claimed in any one of the preceding claims wherein the spring seat (20) comprises an cylindrical portion (30) axially extending from a first circular edge to an opposed second circular edge, the central portion (28) wherein is arranged the central opening inwardly radially extending from the first circular edge and, the peripheral disc portion (32) for receiving the spring (26) outwardly radially extending from the second circular edge.
- High pressure fuel pump (10) as claimed in claim 3 wherein the engagement aperture (34) partially opens in the wall of said cylindrical portion (30).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GBGB1600766.8A GB201600766D0 (en) | 2016-01-15 | 2016-01-15 | Fuel pump |
PCT/EP2017/050281 WO2017121690A1 (en) | 2016-01-15 | 2017-01-06 | Fuel pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3402979A1 EP3402979A1 (en) | 2018-11-21 |
EP3402979B1 true EP3402979B1 (en) | 2020-03-18 |
Family
ID=55488012
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17700137.7A Active EP3402979B1 (en) | 2016-01-15 | 2017-01-06 | Fuel pump |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP3402979B1 (en) |
CN (1) | CN108603478B (en) |
GB (1) | GB201600766D0 (en) |
WO (1) | WO2017121690A1 (en) |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AT312995B (en) * | 1972-04-05 | 1974-01-25 | Friedmann & Maier Ag | Injection pump for internal combustion engines |
DE3605056A1 (en) * | 1986-02-18 | 1987-08-20 | Bosch Gmbh Robert | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
JP4439723B2 (en) * | 2000-12-28 | 2010-03-24 | 株式会社ミクニ | Fuel pump |
JP2003227434A (en) * | 2002-01-31 | 2003-08-15 | Denso Corp | Distribution type fuel injection pump |
US20050100466A1 (en) * | 2003-01-09 | 2005-05-12 | Nobuo Aoki | Fuel supply pump |
JP2008095573A (en) * | 2006-10-10 | 2008-04-24 | Toyota Motor Corp | High-pressure pump |
CN201225273Y (en) * | 2008-06-21 | 2009-04-22 | 施小林 | Novel plunger type injection pump |
CN201381921Y (en) * | 2009-04-09 | 2010-01-13 | 周书田 | Single-cylinder small cylinder bore high-speed diesel engine fuel injection assembly |
ITMI20120270A1 (en) * | 2012-02-23 | 2013-08-24 | Bosch Gmbh Robert | HIGH PRESSURE PUMP FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE |
-
2016
- 2016-01-15 GB GBGB1600766.8A patent/GB201600766D0/en not_active Ceased
-
2017
- 2017-01-06 CN CN201780006322.9A patent/CN108603478B/en active Active
- 2017-01-06 EP EP17700137.7A patent/EP3402979B1/en active Active
- 2017-01-06 WO PCT/EP2017/050281 patent/WO2017121690A1/en active Application Filing
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
---|---|
CN108603478B (en) | 2020-12-11 |
WO2017121690A1 (en) | 2017-07-20 |
EP3402979A1 (en) | 2018-11-21 |
GB201600766D0 (en) | 2016-03-02 |
CN108603478A (en) | 2018-09-28 |
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