EP3209880A1 - Pumping mechanism - Google Patents

Pumping mechanism

Info

Publication number
EP3209880A1
EP3209880A1 EP15763502.0A EP15763502A EP3209880A1 EP 3209880 A1 EP3209880 A1 EP 3209880A1 EP 15763502 A EP15763502 A EP 15763502A EP 3209880 A1 EP3209880 A1 EP 3209880A1
Authority
EP
European Patent Office
Prior art keywords
pump head
sealing assembly
seal
extension section
plunger
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
EP15763502.0A
Other languages
German (de)
French (fr)
Other versions
EP3209880B1 (en
Inventor
Peter Voigt
Onur Mehmet Tansug
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 IP Ltd
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 EP3209880A1 publication Critical patent/EP3209880A1/en
Application granted granted Critical
Publication of EP3209880B1 publication Critical patent/EP3209880B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F02M59/442—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 means preventing fuel leakage around pump plunger, e.g. fluid barriers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0408—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • 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
    • F04B53/02—Packing the free space between cylinders and 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
    • 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
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • F02M2041/1438—Arrangements or details pertaining to the devices classified in F02M41/14 and subgroups
    • F02M2041/1494—Details of cams, tappets, rotors, venting means, specially arranged valves, e.g. in the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for

Definitions

  • the present invention relates to a high pressure fuel pump, and more specifically to a pumping mechanism of a fuel pump actuated by an oil lubricated cam follower.
  • a pumping mechanism 2 of a known high pressure fuel pump such as a unit pump, comprises a pump head 6, provided with a plunger location bore 8, in which a plunger 10 is partially located and restrained in an axial direction by a guide portion 20 of the bore 8.
  • the plunger 10 extends towards a cam follower 12, the cam follower comprising a tappet 14 and a roller 16.
  • a rotating cam (not shown) provides a force to the plunger 10 via the cam follower 12, causing the plunger 10 to move in a reciprocating motion inside the pump head 6, thereby pressurising fuel in a plumping chamber (not shown) provided at an extremity of the bore 8 remote from the cam follower 12.
  • a coil spring 18 is compressed between the cam follower 12 and the pump head 6, and maintains contact between the roller 16 and the cam during a return stoke of the pumping mechanism 2.
  • the plunger 10 is lubricated by fuel inside the guide portion 20 of the plunger location bore 8, whilst a lower extremity of the plunger 10, and the cam follower 12, are lubricated by engine oil. As the plunger 10 reciprocally slides within the pump head 6, small quantities of oil and fuel are caused to mix, thereby generating undesirable pollution.
  • oil in the fuel system has detrimental effect of creating chemicals which leads to filter clogging during the combustion process, and furthermore lacquering of the spray holes of the injector nozzles.
  • Fuel contamination of lubrication oil is of increasing concern in the latest high efficiency engines, as lubrication oil viscosities are decreasing to minimise frictional losses and service intervals are being increased by all engine manufacturers.
  • a known problem with such this type of pump is difficulty in validation of the crimping operation, which must be sufficiently strong to retain the retainer on the pump head, but must also be sufficiently weak so as not distort the match bore, or damage the retainer during the crimping operation.
  • the present invention provides, in a first aspect, a sealing assembly for a high pressure fuel pumping mechanism according to claim 1.
  • the sealing assembly may further comprise means to retain the sealing assembly on the pump head.
  • the extension section of the pump head may comprise a first portion and a second portion, closer to the cam follower than the first portion, wherein part of the seal retainer surrounds the second portion of the extension section, and the retaining means may comprise a weld between the seal retainer and the second portion of the extension section.
  • the second portion of the extension section may have an external diameter which is less than that of the first portion, wherein an axial surface of the seal retainer abuts a shoulder provided at a junction of the first and second sections of the extension section, and the weld may comprise at least a weld seam between the shoulder of the extension section and the surface of the seal retainer which abuts the shoulder.
  • the weld may comprise a weld seam between an external surface of the second portion of the extension section, and an internal surface of the seal retainer which surrounds the second portion.
  • the cam follower may comprise a tappet and a roller provided in a recess of the tappet, wherein the first spring seat is provided by an axial surface of the pump head.
  • the sealing retainer may comprise a deep drawn sheet, or a low carbon tube.
  • the retaining means may alternatively comprise a lip provided on the seal which is located in a recess provided on the extension section of the pump head.
  • the spring retainer may entirely envelop the extension section of the pump head, and the first spring seat may be provided by an axial face of a flange provided at an end of the seal retainer proximate to the main section of the pump head.
  • the present invention comprises a high pressure fuel pumping mechanism comprising a sealing assembly according to the first aspect of the present invention.
  • Figure 2 is a partial cross-sectional view of a pump assembly in accordance with a first embodiment of the present invention
  • Figure 3 is a cross-sectional detailed partial view of the pump assembly of Figure 2;
  • Figure 4 is a partial cross-sectional view of a pump assembly in accordance with a second embodiment of the present invention.
  • FIG. 5 is a cross-section detailed partial view of the pump assembly of
  • a first embodiment of the present invention comprises a pumping mechanism 102 comprising a pump head 106, comprising a main body section 130, and an extension section 132.
  • a pumping chamber (not shown) is provided at a top end of a plunger location bore 108 provided in the pump head 106.
  • a pumping element in the form of a plunger 110 is located partially within the plunger location bore 108, the plunger 110 extending from the pumping chamber, along the extension section 132, and protruding from a base surface 134 of the extension section 132.
  • a guide portion 120 of the plunger location bore 108 bore acts to restrain the plunger 110 within the plunger location bore 108 in an axial direction.
  • a cam follower 112 comprising a tappet 114 and a cam roller 116.
  • a bottom end 140 of the plunger 110 contacts an upper side 150 of the tappet 114, and the cam roller 116 is located in a recess 154 provided on a lower side 152 of the tappet 114.
  • the extension section 132 of the pump head 106 comprises a first portion 136, and a second portion 138, further away from the main body section 130 of the pump head 106, and of a reduced external diameter relative to that of the first portion 136.
  • a junction of the first portion 136 and the second portion 138 forms a shoulder 137 (indicated in Figure 3).
  • the pumping mechanism further 102 comprises a sealing assembly 180, comprising a seal 182 and a seal retainer 184, located within a spring chamber 142.
  • the seal retainer 184 envelops both the first portion 136 and the second portion 138 of the extension section 132 of the pump head 106.
  • the seal retainer is shaped so as to abut the outer surfaces of the first portion 136 and the second portion 138 of the extension section 132, i.e. the seal retainer 184 comprises a first, upper tubular section 186 around the first portion 136 of the extension section 132, and a second, lower tubular section 188 of greater cross-sectional area, around the second portion 138 of the extension section 132.
  • the second, lower tubular section 188 comprises a first, upper portion 190 which surrounds the second portion 138 of the extension section 132, and a second, lower portion 192, which extends below the extension section 132, towards the cam follower 112.
  • the seal 182 is located partially in the lower section 192 of the seal retainer 184, and partially extends below the seal retainer 184, towards the cam follower 112.
  • the seal retainer 184 further comprises a flange 300, which extends perpendicularly to a longitudinal axis A of the plunger location bore 108, and contacts an axial surface 170 of the pump head 106.
  • the extension section In the first embodiment of the present invention, the extension section
  • the 132 of the pump head 106 further comprises an end section 350, which is provided with an annular recess 352 at a point adjacent the second portion 138.
  • the seal 182 is provided with an annular lip 360, of a complementary form to the recess 352.
  • a coil spring 118 is provided in the spring chamber 142 surrounding the extension section 132 of the pump head 106 and part of the plunger 110 extending from the plunger location bore 108.
  • the outer diameter of the flange 300 of the seal retainer 184 is greater than the outer diameter of the spring 118.
  • a first, top end 160 of the spring 118 abuts against a first, upper spring seat provided by an axial face 302 of the flange 300 of the seal retainer 184, and a second, bottom end 162 of the spring 118 abuts at a second, lower spring seat 172 adjacent the tappet 114.
  • the spring retainer 184 is formed of a material having a sufficient hardness to enable the axial face 302 of the flange 300 to act as a spring seat.
  • the spring 118 ensures that, during the return stroke, contact is maintained between the cam roller 116 and the cam. Subsequent pumping and return strokes cause the plunger 110 to move slidably within the plunger location bore 108 in a reciprocating motion.
  • the sealing assembly 180 acts to prevent mixing of fuel which lubricates the plunger 110 inside the plunger location bore 108, with oil which lubricates the cam follower 112 and a lower part
  • the first embodiment of the present invention is improved over the prior art, as a crimping step is not required to retain the sealing assembly 180 in place on the pump head 106.
  • Extension of the seal 182 below, e.g. out of, the seal retainer 184, provides that less material is required to form the seal retainer than in prior art embodiments. Additionally, prior art embodiments required a tight tolerance between the pump head 106 and the seal retainer 184, to allow for thermal expansion of steel components and/or extension of the seal material such as rubber; the tolerance requirement in the present invention is relaxed in comparison to prior art embodiments. This can provide an additional benefit in achieving optimum packaging o f the pump .
  • the present invention also enables provision of a the sealing assembly 180 as a sub assembly. Furthermore, during handling and transportation of subassemblies comprising the sealing assembly 180 and the pump head 106, retention is maintained between the pump head 106 and the sealing assembly 180, due to the cooperation of the lip 360 in the recess 352 of the end section 350 of the extension section 132.
  • FIGS. 4 and 5 illustrate an alternative embodiment of the present invention.
  • the sealing assembly 280 of the second embodiment comprises a seal 282 and a seal retainer 284.
  • the seal retainer 284 comprises a tubular section 288, comprising a first, top portion 290 which surrounds the second portion 138 of the extension section 132 of the pump head 106, and second, lower portion 292, which extends below the extension section 132, towards the cam follower 112.
  • the seal 282 is provided partially in the second, lower portion 288 of the seal retainer 284, and partially extends below the seal retainer 284, towards the cam follower 112.
  • An axial top surface 294 of the upper end of the seal retainer 284 abuts the shoulder 137 formed between the first portion 136 and the second portion 138 of the extension section 132.
  • the seal retainer 284 is welded to the second portion 138 of the extension 132 section by laser weld seam, thereby acting as a retaining means, to retain the sealing assembly 280 on the pump head 106.
  • the weld between the seal retainer 284 and the second portion 138 of the extension section 132 is either between the top surface 294 of the retainer 284 and the shoulder 137 of the extension section 132, between a portion of an internal wall 287 of the seal retainer 184 and an external wall portion 139 of the second portion 138 which is surrounds, or both.
  • the location of, and degree of welding between the seal retainer 284 and the extension section 132 can be selected such that the longitudinal length of the seal 284 retainer, i.e. along the longitudinal axis A of the plunger location bore 108, can be minimised. This is advantageous in minimising material costs, and maximising extension of the seal 282 from the seal retainer 284.
  • the sealing assembly 280 acts to prevent mixing of fuel which lubricates the plunger 110 inside the plunger location bore 108, with oil which lubricates the cam follower 112 and a lower part 111 of the plunger 110 extending below the seal 282.
  • the seal retainer 284 of the second embodiment could be formed by a deep drawn sheet. In an alternative embodiment, the seal retainer 284 could be formed of a low carbon tube.
  • Sealing and retention of the sealing assembly 280 is provided by the welding of the seal retainer 284 onto the extension section 132 of the pump head 106.
  • a sufficiently hard and thick first spring seat is provided by the axial face 302 of the pump head 106.
  • the present invention also enables a cost reduction compared to prior art embodiments, as the seal retainer 284 is a simple component, and can be manufactured from a steel of a lower grade than is necessary for the pump head 106.
  • extension of the seal 282 below, e.g. out of, the seal retainer 284 provides that less material is required to form the seal retainer than in prior art embodiments, and enables a relaxation of tolerances between the pump head 106 and the seal retainer 284.
  • the second embodiment of the present invention also enables provision of a the sealing assembly 280 as a sub assembly. Furthermore, during handling and transportation of sub- assemblies comprising the sealing assembly 280 and the pump head 106, retention is maintained between the pump head 106 and the sealing assembly 280, due to the weld seam.

Abstract

Sealing assembly for a high pressure fuel pumping mechanism, comprising a seal and a seal retainer, wherein the seal partially surrounds an extension section of the pump head and partially extends below the pump head towards a cam follower, and wherein the seal is provided partially within the seal retainer, and extends partially from the seal retainer, the cam follower; means such as a weld seam are provided for retaining the seal retainer on the pump head.

Description

Pumping Mechanism TECHNICAL FIELD
The present invention relates to a high pressure fuel pump, and more specifically to a pumping mechanism of a fuel pump actuated by an oil lubricated cam follower.
BACKGROUND OF THE INVENTION
As illustrated in Figure 1, a pumping mechanism 2 of a known high pressure fuel pump such as a unit pump, comprises a pump head 6, provided with a plunger location bore 8, in which a plunger 10 is partially located and restrained in an axial direction by a guide portion 20 of the bore 8. The plunger 10 extends towards a cam follower 12, the cam follower comprising a tappet 14 and a roller 16. A rotating cam (not shown) provides a force to the plunger 10 via the cam follower 12, causing the plunger 10 to move in a reciprocating motion inside the pump head 6, thereby pressurising fuel in a plumping chamber (not shown) provided at an extremity of the bore 8 remote from the cam follower 12. A coil spring 18 is compressed between the cam follower 12 and the pump head 6, and maintains contact between the roller 16 and the cam during a return stoke of the pumping mechanism 2.
The plunger 10 is lubricated by fuel inside the guide portion 20 of the plunger location bore 8, whilst a lower extremity of the plunger 10, and the cam follower 12, are lubricated by engine oil. As the plunger 10 reciprocally slides within the pump head 6, small quantities of oil and fuel are caused to mix, thereby generating undesirable pollution.
In fuel systems adhering to Euro 6 European emission standard and above, where a particulate filter is provided in the exhaust system, oil in the fuel system has detrimental effect of creating chemicals which leads to filter clogging during the combustion process, and furthermore lacquering of the spray holes of the injector nozzles.
Fuel contamination of lubrication oil is of increasing concern in the latest high efficiency engines, as lubrication oil viscosities are decreasing to minimise frictional losses and service intervals are being increased by all engine manufacturers.
In pump assemblies for older applications with less stringent dilution requirements, separation of oil and fuel has previously been achieved by a controlled clearance between the plunger and the guide portion of the bore in which the plunger is moveable. However, requirements of fuel to oil, and oil to fuel dilution rates are being increasing tightly controlled for new generations of diesel fuel injection pumps. In order to meet new regulations for acceptable dilution of lubrication with fuel (wherein allowable quantities of fuel are typically 1/20 or 1/100 of the allowable quantity under regulations applied to older pump assembly applications), it has become necessary to provide an axial seal 22 as illustrated in Figure 1. In addition to the seal 22, it is necessary to provide a metal retainer 24, attached to the pump head 6 by crimping (at areas 26 as indicated in Figure 1) for placement of the seal 22, and an O-ring seal 28, to seal the interface between the retainer 24 and the pump head 6.
A known problem with such this type of pump is difficulty in validation of the crimping operation, which must be sufficiently strong to retain the retainer on the pump head, but must also be sufficiently weak so as not distort the match bore, or damage the retainer during the crimping operation.
SUMMARY OF THE INVENTION
It is an object of the present invention to provide an improved high pressure fuel pump which at least mitigates the above mentioned problems. „
Accordingly the present invention provides, in a first aspect, a sealing assembly for a high pressure fuel pumping mechanism according to claim 1. The sealing assembly may further comprise means to retain the sealing assembly on the pump head.
The extension section of the pump head may comprise a first portion and a second portion, closer to the cam follower than the first portion, wherein part of the seal retainer surrounds the second portion of the extension section, and the retaining means may comprise a weld between the seal retainer and the second portion of the extension section.
The second portion of the extension section may have an external diameter which is less than that of the first portion, wherein an axial surface of the seal retainer abuts a shoulder provided at a junction of the first and second sections of the extension section, and the weld may comprise at least a weld seam between the shoulder of the extension section and the surface of the seal retainer which abuts the shoulder.
Alternatively or additionally, the weld may comprise a weld seam between an external surface of the second portion of the extension section, and an internal surface of the seal retainer which surrounds the second portion. The cam follower may comprise a tappet and a roller provided in a recess of the tappet, wherein the first spring seat is provided by an axial surface of the pump head.
The sealing retainer may comprise a deep drawn sheet, or a low carbon tube.
The retaining means may alternatively comprise a lip provided on the seal which is located in a recess provided on the extension section of the pump head. The spring retainer may entirely envelop the extension section of the pump head, and the first spring seat may be provided by an axial face of a flange provided at an end of the seal retainer proximate to the main section of the pump head. In a further aspect, the present invention comprises a high pressure fuel pumping mechanism comprising a sealing assembly according to the first aspect of the present invention.
BRIEF DESCRIPTION OF THE DRAWINGS
The present invention is now described by way of example with reference to the accompanying figures, in which: Figure 2 is a partial cross-sectional view of a pump assembly in accordance with a first embodiment of the present invention;
Figure 3 is a cross-sectional detailed partial view of the pump assembly of Figure 2;
Figure 4 is a partial cross-sectional view of a pump assembly in accordance with a second embodiment of the present invention; and
Figure 5 is a cross-section detailed partial view of the pump assembly of
Figure 2.
DESCRIPTION OF THE PREFERRED EMBODIMENTS In the description of the present below, relative terms such as upper, lower, above, below, top and bottom, are used in relation to the Figures only, and are not intended to be limiting.
Referring to Figures 2 and 3, a first embodiment of the present invention comprises a pumping mechanism 102 comprising a pump head 106, comprising a main body section 130, and an extension section 132. At a top end of a plunger location bore 108 provided in the pump head 106, a pumping chamber (not shown) is provided. A pumping element in the form of a plunger 110 is located partially within the plunger location bore 108, the plunger 110 extending from the pumping chamber, along the extension section 132, and protruding from a base surface 134 of the extension section 132. A guide portion 120 of the plunger location bore 108 bore acts to restrain the plunger 110 within the plunger location bore 108 in an axial direction.
Below the plunger 110 is provided a cam follower 112, comprising a tappet 114 and a cam roller 116. A bottom end 140 of the plunger 110 contacts an upper side 150 of the tappet 114, and the cam roller 116 is located in a recess 154 provided on a lower side 152 of the tappet 114.
The extension section 132 of the pump head 106 comprises a first portion 136, and a second portion 138, further away from the main body section 130 of the pump head 106, and of a reduced external diameter relative to that of the first portion 136. A junction of the first portion 136 and the second portion 138 forms a shoulder 137 (indicated in Figure 3).
The pumping mechanism further 102 comprises a sealing assembly 180, comprising a seal 182 and a seal retainer 184, located within a spring chamber 142.
In the embodiment of Figures 2 and 3, the seal retainer 184 envelops both the first portion 136 and the second portion 138 of the extension section 132 of the pump head 106. The seal retainer is shaped so as to abut the outer surfaces of the first portion 136 and the second portion 138 of the extension section 132, i.e. the seal retainer 184 comprises a first, upper tubular section 186 around the first portion 136 of the extension section 132, and a second, lower tubular section 188 of greater cross-sectional area, around the second portion 138 of the extension section 132.
The second, lower tubular section 188 comprises a first, upper portion 190 which surrounds the second portion 138 of the extension section 132, and a second, lower portion 192, which extends below the extension section 132, towards the cam follower 112. The seal 182 is located partially in the lower section 192 of the seal retainer 184, and partially extends below the seal retainer 184, towards the cam follower 112.
The seal retainer 184 further comprises a flange 300, which extends perpendicularly to a longitudinal axis A of the plunger location bore 108, and contacts an axial surface 170 of the pump head 106. In the first embodiment of the present invention, the extension section
132 of the pump head 106 further comprises an end section 350, which is provided with an annular recess 352 at a point adjacent the second portion 138. The seal 182 is provided with an annular lip 360, of a complementary form to the recess 352. Once the sealing assembly has been assembled onto the pump head 106, the annular lip 360 of the seal 182 is urged into the recess 352, thereby acting as a retaining means, to retain the sealing assembly 180 on the pump head 106.
During operation of the pumping mechanism 102 and in a pumping stroke, rotation of a cam (not shown) causes force to be transferred, via the cam roller 116 and tappet 114, to the plunger 110, thereby causing the plunger 110 to move upwardly within the plunger location bore 108, along the longitudinal axis A of the plunger location bore 108, thereby causing fuel in the pumping chamber to become pressurised. During further operation of the pumping mechanism 102 and in a return stroke, on further rotation of the cam, the cam roller 116, tappet 114 and plunger
110 move downwardly. A coil spring 118 is provided in the spring chamber 142 surrounding the extension section 132 of the pump head 106 and part of the plunger 110 extending from the plunger location bore 108. The outer diameter of the flange 300 of the seal retainer 184 is greater than the outer diameter of the spring 118. A first, top end 160 of the spring 118 abuts against a first, upper spring seat provided by an axial face 302 of the flange 300 of the seal retainer 184, and a second, bottom end 162 of the spring 118 abuts at a second, lower spring seat 172 adjacent the tappet 114. The spring retainer 184 is formed of a material having a sufficient hardness to enable the axial face 302 of the flange 300 to act as a spring seat.
The spring 118 ensures that, during the return stroke, contact is maintained between the cam roller 116 and the cam. Subsequent pumping and return strokes cause the plunger 110 to move slidably within the plunger location bore 108 in a reciprocating motion.
During use of the pumping mechanism 102, the sealing assembly 180 acts to prevent mixing of fuel which lubricates the plunger 110 inside the plunger location bore 108, with oil which lubricates the cam follower 112 and a lower part
111 of the plunger 110 extending below the seal 182.
The first embodiment of the present invention is improved over the prior art, as a crimping step is not required to retain the sealing assembly 180 in place on the pump head 106.
Furthermore, there is no requirement for sealing lips or additional O- rings which have been used in prior art embodiments, thereby allowing a further cost reduction, and simpler manufacture, compared to prior art embodiments.
Extension of the seal 182 below, e.g. out of, the seal retainer 184, provides that less material is required to form the seal retainer than in prior art embodiments. Additionally, prior art embodiments required a tight tolerance between the pump head 106 and the seal retainer 184, to allow for thermal expansion of steel components and/or extension of the seal material such as rubber; the tolerance requirement in the present invention is relaxed in comparison to prior art embodiments. This can provide an additional benefit in achieving optimum packaging o f the pump .
The present invention also enables provision of a the sealing assembly 180 as a sub assembly. Furthermore, during handling and transportation of subassemblies comprising the sealing assembly 180 and the pump head 106, retention is maintained between the pump head 106 and the sealing assembly 180, due to the cooperation of the lip 360 in the recess 352 of the end section 350 of the extension section 132.
Figures 4 and 5 illustrate an alternative embodiment of the present invention. In common with the first embodiment, the sealing assembly 280 of the second embodiment comprises a seal 282 and a seal retainer 284. However, the form and assembly of the sealing retainer 284 differs from that of the first embodiment as described below. The seal retainer 284 comprises a tubular section 288, comprising a first, top portion 290 which surrounds the second portion 138 of the extension section 132 of the pump head 106, and second, lower portion 292, which extends below the extension section 132, towards the cam follower 112. The seal 282 is provided partially in the second, lower portion 288 of the seal retainer 284, and partially extends below the seal retainer 284, towards the cam follower 112.
An axial top surface 294 of the upper end of the seal retainer 284 abuts the shoulder 137 formed between the first portion 136 and the second portion 138 of the extension section 132.
The seal retainer 284 is welded to the second portion 138 of the extension 132 section by laser weld seam, thereby acting as a retaining means, to retain the sealing assembly 280 on the pump head 106.
The weld between the seal retainer 284 and the second portion 138 of the extension section 132 is either between the top surface 294 of the retainer 284 and the shoulder 137 of the extension section 132, between a portion of an internal wall 287 of the seal retainer 184 and an external wall portion 139 of the second portion 138 which is surrounds, or both.
The location of, and degree of welding between the seal retainer 284 and the extension section 132 can be selected such that the longitudinal length of the seal 284 retainer, i.e. along the longitudinal axis A of the plunger location bore 108, can be minimised. This is advantageous in minimising material costs, and maximising extension of the seal 282 from the seal retainer 284.
In a similar manner to the first embodiment, during use of the pumping mechanism 102, the sealing assembly 280 acts to prevent mixing of fuel which lubricates the plunger 110 inside the plunger location bore 108, with oil which lubricates the cam follower 112 and a lower part 111 of the plunger 110 extending below the seal 282. The seal retainer 284 of the second embodiment could be formed by a deep drawn sheet. In an alternative embodiment, the seal retainer 284 could be formed of a low carbon tube.
Sealing and retention of the sealing assembly 280 is provided by the welding of the seal retainer 284 onto the extension section 132 of the pump head 106. A sufficiently hard and thick first spring seat is provided by the axial face 302 of the pump head 106. The present invention also enables a cost reduction compared to prior art embodiments, as the seal retainer 284 is a simple component, and can be manufactured from a steel of a lower grade than is necessary for the pump head 106.
Similarly to the first embodiment, in the second embodiment there is no requirement for crimping of the seal retainer to the pump head, nor for sealing lips or additional O-rings which have been used in prior art embodiments, thereby allowing a further cost reduction, and simpler manufacture, compared to prior art embodiments.
Also similarly to the first embodiment, extension of the seal 282 below, e.g. out of, the seal retainer 284, provides that less material is required to form the seal retainer than in prior art embodiments, and enables a relaxation of tolerances between the pump head 106 and the seal retainer 284.
The second embodiment of the present invention also enables provision of a the sealing assembly 280 as a sub assembly. Furthermore, during handling and transportation of sub- assemblies comprising the sealing assembly 280 and the pump head 106, retention is maintained between the pump head 106 and the sealing assembly 280, due to the weld seam.
^ ^
REFERENCES
First embodiment:
pumping mechanism 102
pump head 106
plunger location bore 108
plunger 110
bore guide portion 120
cam follower 1 12
tappet 114
cam roller 116
coil spring 118
main body section 130
extension section 132
extension section base surface 134 plunger bottom end 140
spring chamber 142
tappet upper side 150
tappet lower side 152
recess 154
extension section first portion 136 second portion 138
shoulder 137
spring first, top end 160
spring second, bottom end 162
second, lower spring seat 172
sealing assembly 180
seal 182
seal retainer 184
seal retainer first, upper tubular section 186 second, lower tubular section 188 lower tubular section first, upper portion 190 second, lower portion 192
seal retainer flange 300 Λ„
12 flange axial face 302
pump head end section 350
end section annular recess 352
seal annular lip 360
Second embodiment:
external wall portion 139
sealing assembly 280
seal 282
seal retainer 284
seal retainer internal wall portion 287 seal retainer tubular section 288
tubular section top portion 290
tubular section lower portion 292
axial top surface (upper end of seal retainer) 294

Claims

1. A sealing assembly (180, 280) for a high pressure fuel pumping mechanism (102), the pumping mechanism (102) comprising a pump head (106), a cam follower (112) for cooperating with a rotating cam, and a plunger (110), located partially within a plunger location bore (108) provided in the pump head (106) and extending along a longitudinal axis (A) of the plunger location bore (108);
wherein the pump head (106) comprises a main section (130) and an extension section (132),
wherein a portion (111) of the plunger (110) extends from the extension section (132), and a lower surface at an end (140) of the plunger (110) contacts the cam follower (112);
wherein, in use, during a pumping stroke, rotation of the cam causes force to be transferred to the plunger (110) via the cam follower (112), thereby causing the plunger (110) to move along the plunger location bore (108) and into a pumping chamber, to cause fuel within the pumping chamber to become pressurised; and wherein during a return stroke, a spring provided in a spring chamber (142) surrounding the extension section (132) of the pump head (106), and abutting a first spring seat (170) and a second spring seat (172), maintains contact between the cam follower (112) and the cam;
wherein the sealing assembly (180, 280) comprises a seal (182, 282) and a seal retainer (184, 284),
characterised in that the seal (182, 282) is provided partially within the seal retainer (184, 284), and extends partially from the seal retainer (184, 284), towards the cam follower (112).
2. A sealing assembly (180, 280) as claimed in claim 1, further comprising retaining means to retain the sealing assembly (180, 280) on the pump head (106).
3. A sealing assembly (280) as claimed in claim 2 wherein the extension section (132) of the pump head (106) comprises a first portion (136) and a second portion (138), closer to the cam follower (112) than the first portion (136), and wherein part of the seal retainer (284) surrounds the second portion (138) of the extension section (132);
and wherein the retaining means comprises a weld between the seal retainer (284) and the second portion (138) of the extension section (132).
4. A sealing assembly (180) as claimed in claim 3, wherein the second portion (138) of the extension section (132) has an external diameter which is less than that of the first portion (136), and wherein an axial surface (294) of the seal retainer (284) abuts a shoulder (137) provided at a junction of the first section (136) and the second section (138) of the extension section (132), and wherein the weld comprises at least a weld seam between the shoulder (137) of the extension section (132) and the axial surface (294) of the seal retainer.
5. A sealing assembly (180) as claimed in claim 3 or claim 4 wherein the weld comprises at least a weld seam between an external surface (139) of the second portion (138) of the extension section (132), and an internal surface (287) of the seal retainer (284) which surrounds the second portion (138).
6. A sealing assembly (180) as claimed in any one of claims 2 to 5, wherein the cam follower (112) comprises a tappet (114) and a roller (116) provided in a recess (154) of the tappet, and wherein the first spring seat is provided by an axial surface (170) of the pump head (106).
7. A sealing assembly (180, 280) as claimed in any preceding claim, wherein the sealing retainer (184, 284) comprises a deep drawn sheet.
8. A sealing assembly (180, 280) as claimed in of claims 2 to 6, wherein the sealing retainer (184, 284) comprises a low carbon tube.
9. A sealing assembly (180) as claimed in claim 2, wherein the retaining means comprises a lip (360) provided on the seal (182) which is located in a recess (352) provided on an end section (350) of the extension section (132) of the pump head (106).
10. A sealing assembly (180) as claimed in claim 1, wherein the seal retainer (184) entirely envelops the extension section (132) of the pump head (106), and wherein the first spring seat is provided by an axial face (302) of a flange (300) provided at an end of the seal retainer (184) proximate to the main section (130) of the pump head (106).
11. A high pressure fuel pumping mechanism (102) comprising a sealing assembly (180, 280) according to any one of the preceding claims.
EP15763502.0A 2014-10-21 2015-08-24 Pumping mechanism Active EP3209880B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB1418661.3A GB201418661D0 (en) 2014-10-21 2014-10-21 Pumping Mechanism
PCT/EP2015/069307 WO2016062431A1 (en) 2014-10-21 2015-08-24 Pumping mechanism

Publications (2)

Publication Number Publication Date
EP3209880A1 true EP3209880A1 (en) 2017-08-30
EP3209880B1 EP3209880B1 (en) 2020-10-28

Family

ID=52013326

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15763502.0A Active EP3209880B1 (en) 2014-10-21 2015-08-24 Pumping mechanism

Country Status (5)

Country Link
EP (1) EP3209880B1 (en)
KR (1) KR102357678B1 (en)
CN (1) CN106795845B (en)
GB (1) GB201418661D0 (en)
WO (1) WO2016062431A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6406035B2 (en) * 2015-01-29 2018-10-17 株式会社デンソー High pressure fuel pump

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1471247B1 (en) * 1999-02-09 2006-10-18 Hitachi, Ltd. High pressure fuel supply pump for internal combustion engine
JP3905282B2 (en) * 2000-04-18 2007-04-18 トヨタ自動車株式会社 High pressure pump
JP4304887B2 (en) * 2001-06-19 2009-07-29 株式会社デンソー Fuel supply system for alternative fuels
DE10322598A1 (en) * 2003-05-20 2004-12-09 Robert Bosch Gmbh High-pressure piston pump for internal combustion engine, comprises a holding mechanism, which is radially centered through the cylinder bushing
JP2006170184A (en) * 2004-11-16 2006-06-29 Denso Corp High pressure fuel pump
CN1776215A (en) * 2004-11-16 2006-05-24 株式会社电装 High pressure fuel pump
DE102013207393A1 (en) * 2013-04-24 2014-10-30 Robert Bosch Gmbh Piston pump, in particular high-pressure pump for a fuel system for an internal combustion engine

Also Published As

Publication number Publication date
KR20170072886A (en) 2017-06-27
CN106795845B (en) 2020-04-17
GB201418661D0 (en) 2014-12-03
CN106795845A (en) 2017-05-31
KR102357678B1 (en) 2022-02-03
EP3209880B1 (en) 2020-10-28
WO2016062431A1 (en) 2016-04-28

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