EP3153699A1 - Pumping assembly - Google Patents

Pumping assembly Download PDF

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Publication number
EP3153699A1
EP3153699A1 EP16191550.9A EP16191550A EP3153699A1 EP 3153699 A1 EP3153699 A1 EP 3153699A1 EP 16191550 A EP16191550 A EP 16191550A EP 3153699 A1 EP3153699 A1 EP 3153699A1
Authority
EP
European Patent Office
Prior art keywords
plunger
spring seat
spring
seat member
shoe
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
EP16191550.9A
Other languages
German (de)
French (fr)
Other versions
EP3153699B1 (en
Inventor
Toby J PEDLEY
Matthew Fairbairn
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Delphi International Operations Luxembourg SARL
Original Assignee
Delphi International Operations Luxembourg SARL
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Delphi International Operations Luxembourg SARL filed Critical Delphi International Operations Luxembourg SARL
Publication of EP3153699A1 publication Critical patent/EP3153699A1/en
Application granted granted Critical
Publication of EP3153699B1 publication Critical patent/EP3153699B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F02M59/02—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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical

Definitions

  • the present invention relates to a pumping assembly for a pump, and specifically to a pumping assembly for a high pressure diesel fuel pump.
  • a currently known pumping assembly 2 is illustrated in Figure 1 , and comprises a pumping element in the form of a plunger 4, and a plunger return spring 6 located in a spring chamber 8. Rotation of a cam lobe 80 of a driveshaft assembly causes force to be transferred to the plunger 4 via a roller 14 and a shoe 12, thereby causing the plunger 4 to move in a reciprocating motion, thereby to pressurise fuel within a control chamber.
  • the components which transfer rotational movement of the cam lobe 80 to the plunger 4 must be in contact with each other at all times.
  • the spring 6 maintains contact between the roller 14 and the cam lobe 80 by acting through a spring seat 10, which is rigidly mounted on the plunger 4.
  • a secondary function of the spring seat 10 is to act as a guide for a lower end of the spring 6, maintaining it concentrically with the upper end of the spring 6.
  • the spring forces are transferred through the spring seat 10/plunger 4 assembly which thus experiences the spring forces, both axial and radial, during the filling and pumping strokes.
  • a disadvantage of this prior art embodiment is that radial spring force / side load applied to the plunger 4 via contact between the spring seat 10 and the plunger 4, can cause wear, and possibly eventual seizure, of the plunger 4.
  • the present invention provides, in a first aspect, a pumping assembly according to claim 1.
  • the pumping assembly may further comprise a shoulder member which is coupled to the plunger at or near the second end of the plunger; wherein the surface against which the end of the spring remote from the housing part abuts is provided on a radial section of the spring seat member; wherein the radial section of the spring seat member is located between the shoulder member and the housing part; wherein the surface of the spring seat member which abuts the shoe comprises a surface of an axial section of the spring seat member; and wherein the shoulder member is located in a void between the axial section of the spring seat member, and the plunger.
  • a top face of the shoe proximate the plunger and remote from the roller, is non-orthogonal to the pumping axis.
  • the present invention comprises a pumping assembly 102.
  • the pumping assembly 102 comprises a pumping element in the form of a plunger 104, and a spring 106 located in a spring chamber 108.
  • the plunger 104 is located such that a first, upper end 150 thereof is located within a housing part 190, and a second, lower end 152 is located proximate a shoe 112.
  • the shoe 112 is located within a void 160 of a shoe guide 116.
  • Rotation of a cam lobe 180 of a driveshaft assembly causes force to be transmitted to the plunger 104, via a roller 114 and the shoe 112.
  • the transferred force causes the plunger 104 to move in a reciprocating motion along a pumping axis A.
  • the spring 106 comprises a first, upper end 170, proximate the housing part 190, and a second, lower end 172, remote from the housing part 190 and proximate the shoe 112.
  • a spring seat member 120 is located around the plunger 104.
  • a shoulder member 140 is also located around the plunger 104, at or towards the lower end 152 of the plunger 104.
  • the spring seat member 120 comprises a radial section 122, remote from the shoe 112, which extends radially with respect to the pumping axis A, and an axial section 124, between the radial section 122 and the shoe 112, which extends axially with respect to the pumping axis A.
  • the axial section 124 extends from a junction 136 with the radial section 122, toward the shoe 112, and a void 126 is present between the axial section 124 and the plunger 104.
  • the radial section 122 includes an upper surface 128 (i.e. a surface facing the housing part 190), against which the lower end 172 of the spring 106 abuts; the upper surface 128 of the radial section 122 of the spring seat member 120 therefore acts as a spring seat.
  • the spring seat member 120 is located directed on the shoe 112, i.e. such that a lower surface 132 of the axial section 124 of the spring seat member 120, remote from the housing part 190, abuts a top surface 164 of the shoe 112 remote from the roller 114.
  • the plunger 104 protrudes through a clearance through hole 134 provided in the spring seat member 120. Due to a clearance fit between the spring seat member through hole 134 and the plunger 104, the plunger 104 is not coupled to the spring seat member 120.
  • the shoulder member 140 is coupled to the plunger 104 towards the lower end 152 of the plunger 104, for example in an interference fit.
  • the shoulder member 140 is located further away from the housing part 190 than the radial section 122 of the spring seat member 120, such that the radial section 122 of the spring seat member 120 is located between the housing part 190 and the shoulder member 140.
  • the spring force of the spring 106 acts on the spring seat member 120, urging it downwardly. Abutment of a lower surface 130 of the radial section 122 of the spring seat member 120, against an upper surface 144 of the shoulder member 140, causes a corresponding downward movement of the shoulder member 140, and therefore also of the plunger 104 to which the shoulder member 140 is coupled.
  • FIG. 5 A further optional feature of the present invention is illustrated in Figure 5 .
  • all other components are as the first embodiment, except for the shoe 212.
  • a top surface 264 of the alternative shoe 212, remote from the roller 114, is angled, i.e. is non-orthogonal with respect to the pumping axis A. (The angling of the surface 264 is accentuated in Figure 5 for ease of illustration).
  • side-loading on the shoe 212 during use of the pumping assembly 202 as spring forces are amplified by the angling of the shoe top surface 264, thereby to counter side loads.
  • spring force from the plunger return spring 106 is transferred to the shoe 112 through the spring seat member 120.
  • the spring seat member 120 is not coupled to the plunger 104 as in the prior art embodiment. This is advantageous in that the spring seat member 120 adds a stabilising action on the shoe 112, restricting tilting of the shoe 122 and any resulting side load, due to the radius at which the spring force acts.
  • a further advantage of the present invention is that the a fluid film is reestablished around the circumference of the plunger 104.
  • the plunger 104 will have been forced to adopt a certain position/orientation by the pumping forces and plunger return spring forces. If the magnitude and direction of the plunger return spring forces are such that the plunger 104 remains in this position during the filling stroke, then fresh fluid will not have been able to find its way between the plunger 104 and the bore of the housing part 190 in which it is located, at the positions of contact, before the next pumping stroke commences.
  • spring forces are no longer acting on the plunger 104 during the filling stroke, i.e. the plunger 104 is not restrained radially, and the plunger 104 is therefore able to self-centre during a filling stroke. Fluid is therefore able to find its way between the plunger 104 and the bore.

Landscapes

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

Abstract

A pumping assembly for a high pressure diesel fuel pump comprises a spring seat member (120) against which a plunger return spring (106) abuts, and a shoulder member (140) which is coupled to the plunger (104); wherein the plunger (104) protrudes through a clearance through hole (134) of the spring seat member (140) such that the plunger is decoupled from the spring seat member (120) so that spring forces do not act on the plunger (104) and it is able to self-centre during operation of the pump. The pumping assembly further comprises a shoe (112), a top face (164) of which being non-orthogonal to a pumping axis (A).

Description

    TECHNICAL FIELD
  • The present invention relates to a pumping assembly for a pump, and specifically to a pumping assembly for a high pressure diesel fuel pump.
    • BACKGROUND OF THE INVENTION
  • A currently known pumping assembly 2 is illustrated in Figure 1, and comprises a pumping element in the form of a plunger 4, and a plunger return spring 6 located in a spring chamber 8. Rotation of a cam lobe 80 of a driveshaft assembly causes force to be transferred to the plunger 4 via a roller 14 and a shoe 12, thereby causing the plunger 4 to move in a reciprocating motion, thereby to pressurise fuel within a control chamber.
  • The components which transfer rotational movement of the cam lobe 80 to the plunger 4 must be in contact with each other at all times. The spring 6 maintains contact between the roller 14 and the cam lobe 80 by acting through a spring seat 10, which is rigidly mounted on the plunger 4. A secondary function of the spring seat 10 is to act as a guide for a lower end of the spring 6, maintaining it concentrically with the upper end of the spring 6.
  • The spring forces are transferred through the spring seat 10/plunger 4 assembly which thus experiences the spring forces, both axial and radial, during the filling and pumping strokes.
  • A disadvantage of this prior art embodiment is that radial spring force / side load applied to the plunger 4 via contact between the spring seat 10 and the plunger 4, can cause wear, and possibly eventual seizure, of the plunger 4.
    • SUMMARY OF THE INVENTION
  • It is an object of the present invention to provide a pumping assembly which at least mitigates the problems encountered with known embodiments.
  • Accordingly the present invention provides, in a first aspect, a pumping assembly according to claim 1.
  • The pumping assembly may further comprise a shoulder member which is coupled to the plunger at or near the second end of the plunger;
    wherein the surface against which the end of the spring remote from the housing part abuts is provided on a radial section of the spring seat member; wherein the radial section of the spring seat member is located between the shoulder member and the housing part;
    wherein the surface of the spring seat member which abuts the shoe comprises a surface of an axial section of the spring seat member; and wherein the shoulder member is located in a void between the axial section of the spring seat member, and the plunger.
  • In one embodiment, a top face of the shoe, proximate the plunger and remote from the roller, is non-orthogonal to the pumping axis.
    • BRIEF DESCRIPTION OF THE DRAWINGS
  • The present invention is now described by way of example with reference to the accompanying drawings in which:
    • Figure 2 is a longitudinal cross-sectional view of a pumping assembly in accordance with a first embodiment of the present invention;
    • Figure 3 is a cross-sectional partial view of the pumping assembly of Figure 2;
    • Figure 4 is an isometric partial cross-sectional view of the pumping assembly of Figure 2
      and
    • Figure 5 is a longitudinal cross-sectional view of a pumping assembly in accordance with a second embodiment of the present invention.
    DESCRIPTION OF THE PREFERRED EMBODIMENTS
  • An embodiment of the present invention is described below in relation to the orientation of the figures. Terms such as upper, lower, upwards, downwards, above and below are not intended to be limiting.
  • Referring to Figure 2, the present invention comprises a pumping assembly 102. The pumping assembly 102 comprises a pumping element in the form of a plunger 104, and a spring 106 located in a spring chamber 108.
  • The plunger 104 is located such that a first, upper end 150 thereof is located within a housing part 190, and a second, lower end 152 is located proximate a shoe 112. The shoe 112 is located within a void 160 of a shoe guide 116.
  • Rotation of a cam lobe 180 of a driveshaft assembly causes force to be transmitted to the plunger 104, via a roller 114 and the shoe 112. The transferred force causes the plunger 104 to move in a reciprocating motion along a pumping axis A.
  • The spring 106 comprises a first, upper end 170, proximate the housing part 190, and a second, lower end 172, remote from the housing part 190 and proximate the shoe 112.
  • A spring seat member 120 is located around the plunger 104. A shoulder member 140 is also located around the plunger 104, at or towards the lower end 152 of the plunger 104.
  • Referring to the detailed view of Figure 3, the spring seat member 120 comprises a radial section 122, remote from the shoe 112, which extends radially with respect to the pumping axis A, and an axial section 124, between the radial section 122 and the shoe 112, which extends axially with respect to the pumping axis A.
  • The axial section 124 extends from a junction 136 with the radial section 122, toward the shoe 112, and a void 126 is present between the axial section 124 and the plunger 104.
  • The radial section 122 includes an upper surface 128 (i.e. a surface facing the housing part 190), against which the lower end 172 of the spring 106 abuts; the upper surface 128 of the radial section 122 of the spring seat member 120 therefore acts as a spring seat.
  • The spring seat member 120 is located directed on the shoe 112, i.e. such that a lower surface 132 of the axial section 124 of the spring seat member 120, remote from the housing part 190, abuts a top surface 164 of the shoe 112 remote from the roller 114.
  • The plunger 104 protrudes through a clearance through hole 134 provided in the spring seat member 120. Due to a clearance fit between the spring seat member through hole 134 and the plunger 104, the plunger 104 is not coupled to the spring seat member 120.
  • The shoulder member 140 is coupled to the plunger 104 towards the lower end 152 of the plunger 104, for example in an interference fit. The shoulder member 140 is located further away from the housing part 190 than the radial section 122 of the spring seat member 120, such that the radial section 122 of the spring seat member 120 is located between the housing part 190 and the shoulder member 140.
  • On a filling stroke of the pumping assembly 102, the spring force of the spring 106 acts on the spring seat member 120, urging it downwardly. Abutment of a lower surface 130 of the radial section 122 of the spring seat member 120, against an upper surface 144 of the shoulder member 140, causes a corresponding downward movement of the shoulder member 140, and therefore also of the plunger 104 to which the shoulder member 140 is coupled.
  • A further optional feature of the present invention is illustrated in Figure 5. In this embodiment of a pumping assembly 202, all other components are as the first embodiment, except for the shoe 212. A top surface 264 of the alternative shoe 212, remote from the roller 114, is angled, i.e. is non-orthogonal with respect to the pumping axis A. (The angling of the surface 264 is accentuated in Figure 5 for ease of illustration). In this embodiment, side-loading on the shoe 212 during use of the pumping assembly 202, as spring forces are amplified by the angling of the shoe top surface 264, thereby to counter side loads.
  • In the present invention, spring force from the plunger return spring 106 is transferred to the shoe 112 through the spring seat member 120. The spring seat member 120 is not coupled to the plunger 104 as in the prior art embodiment. This is advantageous in that the spring seat member 120 adds a stabilising action on the shoe 112, restricting tilting of the shoe 122 and any resulting side load, due to the radius at which the spring force acts.
  • A further advantage of the present invention is that the a fluid film is reestablished around the circumference of the plunger 104. During a pumping stroke, the plunger 104 will have been forced to adopt a certain position/orientation by the pumping forces and plunger return spring forces. If the magnitude and direction of the plunger return spring forces are such that the plunger 104 remains in this position during the filling stroke, then fresh fluid will not have been able to find its way between the plunger 104 and the bore of the housing part 190 in which it is located, at the positions of contact, before the next pumping stroke commences. With the de-coupled plunger 104 of the present invention, spring forces are no longer acting on the plunger 104 during the filling stroke, i.e. the plunger 104 is not restrained radially, and the plunger 104 is therefore able to self-centre during a filling stroke. Fluid is therefore able to find its way between the plunger 104 and the bore.
    • REFERENCES Prior art
    • pumping assembly 2
    • plunger 4
    • spring 6
    • spring chamber 8
    • spring seat 10
    • shoe 12
    • roller 14
    • cam lobe 80
    Invention
    • pumping assembly 102, 212
    • plunger 104
    • spring 106
    • spring chamber 108
    • shoe 112
    • roller 114
    • spring seat member 120
    • spring seat member radial section 122
    • spring seat member axial section 124
    • axial section void 126
    • radial section upper surface 128
    • radial section lower surface 130
    • axial section lower surface 132
    • spring seat member clearance through hole 134
    • spring seat member junction 136
    • shoulder member 140
    • plunger first, upper end 150
    • plunger second, lower end 152
    • spring seat member void 160
    • shoe top surface 164, 264
    • spring upper end 170
    • spring lower end 172
    • cam lobe 180
    • housing part 190
    • pumping axis A

Claims (1)

  1. A pumping assembly (102) comprising a plunger (104) and a spring (106) located within a spring chamber (108), wherein a first end (150) of the plunger (104) is located within a housing part (190), and a second end (152) of the plunger (104) remote from the first end (150) is proximate a shoe (112, 212), and wherein reciprocating movement of the plunger (104) along a pumping axis (A) is caused by force transferred from a rotating cam lobe (180), via a roller (114) and a shoe (112,212);
    the pumping assembly (102) further comprising spring seat member (120) comprising a surface (128) against which an end (172) of the spring (106) remote from the housing part (190) abuts; the spring seat member (120) further comprising a surface (132) which abuts the shoe (112, 212);
    wherein the plunger (104) is located within a through hole (134) of the spring seat member (120) and wherein a clearance fit exists between the spring seat member through hole (134) and the plunger (104);
    the pumping assembly (102) further comprising a shoulder member (140) which is coupled to the plunger (104) at or near the second end (152) of the plunger;
    wherein the surface (128) against which the end (172) of the spring (106) remote from the housing part (190) abuts is provided on a radial section (122) of the spring seat member (120); wherein the radial section (122) of the spring seat member (120) is located between the shoulder member (140) and the housing part (190);
    wherein the surface (132) of the spring seat member (120) which abuts the shoe (112, 212) comprises a surface (130) of an axial section (124) of the spring seat member (120); and wherein the shoulder member (140) is located in a void (126) between the axial section (122) of the spring seat member (120), and the plunger (104);
    wherein the shoe (212) comprises a top face (264), proximate the plunger (104) and remote from the roller (114), and wherein the top face (264) of the shoe (212) is non-orthogonal to the pumping axis (A).
EP16191550.9A 2015-10-05 2016-09-29 Pumping assembly Active EP3153699B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GBGB1517504.5A GB201517504D0 (en) 2015-10-05 2015-10-05 Pumping assembly

Publications (2)

Publication Number Publication Date
EP3153699A1 true EP3153699A1 (en) 2017-04-12
EP3153699B1 EP3153699B1 (en) 2018-05-23

Family

ID=54606052

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16191550.9A Active EP3153699B1 (en) 2015-10-05 2016-09-29 Pumping assembly

Country Status (3)

Country Link
EP (1) EP3153699B1 (en)
KR (1) KR102615466B1 (en)
GB (1) GB201517504D0 (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030180159A1 (en) * 2002-03-21 2003-09-25 Gerd Blessing Piston pump
EP2476895A2 (en) * 2011-01-14 2012-07-18 Hitachi Automotive Systems, Ltd. High pressure fuel supply pump
JP2012202212A (en) * 2011-03-23 2012-10-22 Toyota Motor Corp Fuel pump and fuel supply device
DE102013224797A1 (en) * 2013-12-04 2015-06-11 Robert Bosch Gmbh Fuel pump with a piston, at its end facing a drive end a spring divider is arranged

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10344459B4 (en) * 2003-09-25 2012-06-14 Robert Bosch Gmbh Piston pump, in particular high-pressure piston pump
EP2660459B1 (en) * 2012-05-03 2016-04-06 Delphi International Operations Luxembourg S.à r.l. Load reduction

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030180159A1 (en) * 2002-03-21 2003-09-25 Gerd Blessing Piston pump
EP2476895A2 (en) * 2011-01-14 2012-07-18 Hitachi Automotive Systems, Ltd. High pressure fuel supply pump
JP2012202212A (en) * 2011-03-23 2012-10-22 Toyota Motor Corp Fuel pump and fuel supply device
DE102013224797A1 (en) * 2013-12-04 2015-06-11 Robert Bosch Gmbh Fuel pump with a piston, at its end facing a drive end a spring divider is arranged

Also Published As

Publication number Publication date
EP3153699B1 (en) 2018-05-23
KR102615466B1 (en) 2023-12-19
GB201517504D0 (en) 2015-11-18
KR20170040760A (en) 2017-04-13

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