EP3073110B1 - Ensemble de pompe - Google Patents

Ensemble de pompe Download PDF

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Publication number
EP3073110B1
EP3073110B1 EP16157228.4A EP16157228A EP3073110B1 EP 3073110 B1 EP3073110 B1 EP 3073110B1 EP 16157228 A EP16157228 A EP 16157228A EP 3073110 B1 EP3073110 B1 EP 3073110B1
Authority
EP
European Patent Office
Prior art keywords
bearing
driveshaft
chamber
rider
cambox
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
Application number
EP16157228.4A
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German (de)
English (en)
Other versions
EP3073110A1 (fr
Inventor
James McHattie
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
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Filing date
Publication date
Application filed by Delphi International Operations Luxembourg SARL filed Critical Delphi International Operations Luxembourg SARL
Publication of EP3073110A1 publication Critical patent/EP3073110A1/fr
Application granted granted Critical
Publication of EP3073110B1 publication Critical patent/EP3073110B1/fr
Active legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • 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
    • F04B53/08—Cooling; Heating; Preventing freezing
    • 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
    • F04B53/18—Lubricating

Definitions

  • the present invention relates to a pump assembly for use in an internal combustion engine, and particularly to lubrication and cooling in a high pressure pump.
  • FIG. 1 A known embodiment of high pressure pump assembly is partially illustrated in Figure 1 , and schematically illustrated in Figure 2 .
  • the pump assembly 2 comprises pump housing 4 ( Figure 2 ), and a driveshaft 6 which is rotatable within the pump housing 4.
  • the driveshaft 6 comprises a cam portion 10, located in a cambox 8 of the pump housing 4, a front journal portion 20 and a rear journal portion 22. Rotation of the driveshaft 6 causes the cam portion 10 to impart force, for example via a cam rider and cam follower, to one or more pumping elements such as plungers.
  • the driveshaft is supported within the pump housing 4 by bearings, such as a front bearing 40 and a rear bearing 42 (only shown in Figure 1 ).
  • an inlet 16 is supplied by a lift pump 54; the inlet 16 supplies fuel for a high pressure circuit 102 via an inlet metering valve (IMV) 46 and also supplies fuel directly to the cambox 8 via an entry 88.
  • IMV inlet metering valve
  • the cambox 8 is pressurised, to allow leakage past the bearing clearances.
  • the leakage is evacuated to a backleak path, via a cambox exit 96 and orifice 98.
  • leakage is also evacuated to the backleak path via an axial drilling 34 provided in the drive shaft 6.
  • Low pressure is maintained in the circuit by a seal 82, which is also linked to the backleak path, via a radial drilling 66 (shown in Figure 1 ) provided in the driveshaft 6, which communicates with the axial drilling 34.
  • the fuel is at lift pump pressure in the entry 88 and in the cambox 8.
  • the known pump assembly of Figures 1 and 2 force feeds the bearings, thereby providing them with adequate flow to prolong durability of the pump.
  • the known embodiment does not allow higher temperature fuel from plunger leakage to pass over the bearing surfaces.
  • debris from component wear is unable to pass over the surfaces of the bearings. The life of the bearing surfaces of the prior art embodiment is therefore limited.
  • Cambox debris may also block an orifice of the exit from the cambox, thereby increasing the temperature of the cambox and increasing the amount of heat transferred to the bearing surfaces, and thereby presenting difficulty in maintaining the bearing material, for example polyether ether ketone (PEEK), at a reduced temperature.
  • PEEK polyether ether ketone
  • the present invention provides, in a first aspect, a pump assembly according to claim 1.
  • the chamber of the pump assembly may be in fluid communication with a rear bearing and a rear journal surface over which the rear bearing is located, wherein the chamber is also in fluid communication, via drillings provided in the driveshaft, with a front bearing and a front journal surface of the front journal over which the front bearing is located, and/or with a rider bearing and a rider bearing surface of the cam portion over which the rider bearing is located.
  • the drillings provided in the driveshaft may comprise an axial drilling, a first radial drilling provided in the cam portion, and a second radial drilling provided in the front journal portion, wherein the axial drilling communicates the first radial drilling and the second radial drilling with the chamber, the first radial drilling communicates the axial drilling with the rider bearing and the rider journal surface, and the second radial drilling communicates the axial drilling with the front bearing and front journal surface.
  • Fuel flowing from the chamber via the rear bearing and rear journal surface, and via the rider bearing and rider journal surface, may flow into a volume within the cambox, wherein fuel flowing from the chamber via the front bearing and front journal surface flows either into the volume with the cambox or into an annular gallery provided within the pump housing around the driveshaft, and wherein the backleak path comprises, a first exit pathway section providing unrestricted fluid communication between the volume within the cambox and a common backleak pathway section; and a second exit pathway section, providing fluid communication between the gallery and the common backleak pathway section.
  • the second exit pathway section may be provided by a drilling having a cross-sectional area which is less than a cross-sectional area of the first pathway section.
  • the pump assembly may further comprise at least one channel provided in the pump housing and leading from the chamber to the cambox.
  • a throttle comprising a section of channel having a reduced cross-sectional area, may be provided in the or each channel.
  • the present invention comprises a pump assembly 102 for a vehicle fuel system, the pump assembly 102 comprising a pump housing 104 and a driveshaft 106, which is rotatable within the pump housing 104, thereby to cause a reciprocating motion of one or more pumping elements (not shown) of a pump head.
  • the embodiment illustrated in Figures 3 and 4 includes a first pump head 112 and a second pump head 114.
  • the driveshaft 106 comprises a front journal portion 120 towards a first, front end 130 of the driveshaft 106, and a rear journal portion 122 towards a second, rear end 132 of the driveshaft 106.
  • the driveshaft 106 further comprises a cam portion 110, between the front and rear journal portions 120, 122, and within a cambox 108 of the pump housing 104.
  • the driveshaft is supported within the pump housing 104 by bearings.
  • a front bearing 140 is located over a front journal surface 126 of the front journal portion 120
  • a rear bearing 142 is located over a rear journal surface 128 of the rear journal portion 122
  • a rider bearing 144 is located over a rider journal surface 124 of the cam portion 110.
  • An inlet 116 supplied with fuel from a fuel tank 150 via a filter 152 and lift pump 154, provides fuel to at high pressure (for example 4 bar), to a high pressure circuit 202, via an IMV 146.
  • the inlet 116 also supplies high pressure fuel to the pump housing 104, via an entry 164.
  • Fuel from the fuel tank 150 is the cleanest, i.e. has fewer debris particles, and is at a lower temperature, than other fuel in the vehicle fuel system.
  • the inlet 116 supplies fuel, via the entry 164, to a chamber 158.
  • the chamber 158 comprises an area behind the second, rear end 132 of the driveshaft 106, i.e. behind the rear journal portion 122 of the driveshaft 106.
  • the chamber 158 communicates with the clearances of the rear bearing 142. Clean, filtered, and low temperature fuel supplied to the chamber 158 therefore is forced through the clearances of the rear bearing 142, i.e. between the rear bearing 142 and the rear journal surface 128 of the driveshaft 106, and between the rear bearing 142 and the pump housing 104, to the cambox 108.
  • the forced flow of fuel over the rear bearing 142 is shown schematically by the arrowed line X, above the rear bearing 142 in Figure 4 .
  • Fuel from the chamber 158 also flow into an axial drilling 134, which is provided partially through the centre of the driveshaft 106.
  • the driveshaft 106 further comprises a first radial drilling 136, through the cam portion 110, which communicates the axial drilling 134 with a cambox volume 118. Clean, filtered, and low temperature fuel from the inlet is therefore also force fed from the chamber 158 to the cambox volume 118, via the axial drilling 134 and the first radial drilling 136, thereby lubricating and cooling the rider journal surface 124 and the rider bearing 144.
  • the forced flow of fuel over the rider bearing 144 is shown schematically by the arrowed line Y, above the rider bearing 144 in Figure 4 .
  • the driveshaft 106 also comprises a second radial drilling 138, through the front journal portion 120, which communicates the axial drilling 134 with the front journal surface 126.
  • Clean, filtered, and low temperature fuel from the inlet 116 is therefore also force fed from the chamber 158 through the clearances of the front bearing 140, i.e. between the front bearing 140 and the front journal surface 126 of the driveshaft 106, and between the front bearing 140 and the pump housing 104.
  • Fuel being force fed to the front journal surface 126 and the front bearing 140 flows (to the right in the orientation of the Figures) into the cambox 108, or (to the left in the orientation of the Figures) into an annular gallery 180, provided in the pump housing 104 towards the first, front end 30 of the driveshaft 106. (The annular gallery 180 is only indicated in Figure 3 ).
  • the forced flow of fuel over the front bearing 140 is shown schematically in Figure 2 by the arrowed line Z, above the front bearing 140 in Figure 4 .
  • annular gallery 180 is sealed by a seal 182 provided around the driveshaft 106 towards the first, front end 130.
  • the seal 182 operates at backleak pressure, which could typically be 0.5 bar.
  • the first radial drilling 136 and the second radial drilling 138 are not dependent upon each other, i.e. a first radial drilling 136 could be provided and a second radial drilling 138 omitted, or vice versa.
  • the rider journal surface 124 and/or rider bearing 144 is force fed with fuel from the chamber 158.
  • the flow required by the lift pump 154 would be advantageously reduced, however disadvantages of a non-pressure fed rider journal would be present.
  • the present invention may optionally comprise one or more fuel take-offs, i.e. channels, leading from the chamber 158 to the cambox volume 118 surrounding the rider journal surface 124 of the driveshaft 106.
  • a first fuel take-off channel 160 and a second fuel take-off channel 162 are provided.
  • the first fuel take-off channel 160 communicates the chamber 158 with a region of the cambox volume 118 between the first pump head 112 and the rider journal surface 124 of the driveshaft 106.
  • the second fuel take-off channel 162 is provided which communicates the chamber 158 and a region of the cambox volume 118 between the second pump head 114 and the rider journal 124 of the driveshaft 106.
  • a first throttle 170 and a second throttle 172 are provided in the first channel 160 and the second channel 162 respectively.
  • the throttles 170, 172 comprise reduced diameter drillings, i.e. sections of the channels 160, 162 having a reduced cross-sectional area.
  • the driveshaft 106 interfaces with the pump heads 112, 114 within the cambox volume 118, for example, via a cam rider / cam follower interface (not shown).
  • a cam rider / cam follower interface (not shown).
  • Such interfaces are subject to very high temperature fuel from pumping element leakage.
  • the clean, filtered and low temperature fuel supplied from the inlet 116 via the channels 160, 162 acts to cool the interfaces. Cooling of the interfaces, even by a relatively small amount, provides improvements in the durability of the pump assembly 104.
  • the size of the axial drilling 134 and the radial drillings 136, 138 in the driveshaft 106 are selected so as to throttle the flow of fuel from the inlet 116, thereby to provide adequate bearing cooling, whilst maintaining a high efficiency of the lift pump 154.
  • Fuel which has been forced into the cambox volume 118 and into the annular gallery 180 via the bearing surfaces is evacuated back to the fuel tank 150 via a backleak path.
  • the backleak path comprises a first exit pathway section 190, which communicates the cambox volume 118 with a common pathway section 194, and a second exit pathway section 192, which communicates the annular gallery 180 with the common pathway section 194.
  • the common pathway section 194 communicates the first and second exit pathway sections 190, 192 with the fuel tank 150, i.e. backleak from the system is returned to the fuel tank 150.
  • the common pathway section 194 and the first backleak section 190 are drilled to the largest possible diameters given dimensioning constraints of the pump housing 104, and specifically, a backleak pathway route from the cambox volume 118 the common pathway section 194 and first backleak section 190 do not contain the orifice of the prior art embodiment. Resistance to the lift pump 154 (via the bearing clearances) is thereby minimised, thereby providing potential further reduction in CO2 emissions.
  • first backleak section 190 communicates directly with the cambox volume 118, leakage from the pumping element, i.e. increased temperature leakage, is evacuated from the cambox volume 118 without passing over the surfaces of the bearings 140, 142, 144 thereby preventing any further increase in the temperature of the bearings 140, 142, 144.
  • the first exit path section 190 and common pathway section 194 comprise an unrestricted channel from the cambox 108 to the backleak, there is no opportunity for blockage. Therefore, there is no requirement for a stucken filter in the present invention, as an unrestricted path is provided for debris to be evacuated from the pump assembly 102.
  • the second backleak pathway section 192 comprises a relatively narrow drilling, i.e. the cross-sectional area of the second backleak pathway section 192 has a smaller cross-sectional area than that of the first exit pathway section 190 and the common pathway section 194. This acts to reduce pressure spikes occurring due to fluctuations in the cambox volume 118, for example as a result of pumping element leakage.
  • the specific diameter of the second backleak pathway section 192 will depend upon the clearance of the bearings 140, 142, however could typically be approximately 1mm to 2 mm.
  • fuel flowing through the in the entry 164, the chamber 158, sections of the channels 160, 162 between the chamber 158 and throttles 170, 172, the axial driveshaft drilling 126, and the radial driveshaft drillings 134, 136 is at high pressure, i.e. lift pump pressure. Due to the reduction of pressure by the throttles 170, 172 and the effect of the fuel squeezing through the bearing clearances, fuel in the sections of the channels 160, 162 between throttles 170, 172, in the cambox volume 118, in the annular gallery 136, and in the backleak circuit 192, 190, 194, is at low pressure, i.e. backleak pressure.
  • the present invention provides a positive driveshaft low pressure circuit, providing force-fed lubrication and cooling of the bearings 140, 142, 144 during a hydrodynamic filling stage, which is further pressurised by hydrodynamic support action of the bearings 140, 142, 144.
  • Force-feeding fuel to the rider journal surface 124 acts to increase the load bearing capacity of the rider journal portion 122.
  • the life of a PTFE bearing could therefore be extended, or alternatively PEEK material could be used for the rider bearing 144.
  • the lubrication and cooling fuel circuit of the present invention provides a bearing-biased lubricating flow of the lowest temperature, cleanest fuel available to the pump assembly 102.
  • the present invention thereby improves the durability of PEEK material bearings by reducing the opportunity for material creep caused by heat.
  • the load capacity of the bearings 140, 142, 144 can therefore be increased, allowing for the use of bearings of a reduced diameter, and accordingly a decrease in pump packaging volume.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (3)

  1. Ensemble formant pompe à haute pression (108) comprenant un boîtier de pompe (104) et un arbre d'entraînement (106) qui est capable de rotation à l'intérieur du boîtier de pompe (104), l'arbre d'entraînement (106) comprenant une portion à palier lisse avant (120), une portion à palier lisse arrière (122), et une portion en came (110), située entre la portion à palier lisse avant (120) et la portion à palier lisse arrière (122) et à l'intérieur d'une boîte à came (108) du boîtier de pompe (104) ;
    dans lequel une rotation de l'arbre d'entraînement (106) amène la portion en came (110) à imposer une force sur un élément de pompage d'au moins une tête de pompe (112, 114) et à provoquer un mouvement en va-et-vient dudit élément de pompage ;
    dans lequel l'arbre d'entraînement (106) est supporté dans le boîtier de pompe (104) par au moins un palier (140, 142, 144) situé sur une surface de palier lisse (124, 126, 128) de l'arbre d'entraînement (106) ;
    dans lequel le boîtier de pompe (104) comprend une chambre (158) adjacente à une extrémité (132) de l'arbre d'entraînement (106), dans lequel la chambre (158) est alimentée avec du carburant depuis une entrée (116) qui est alimentée par un réservoir de carburant (150), et dans lequel la chambre (158) est en communication fluidique avec au moins un palier (140, 142, 144), et au moins une surface à palier lisse (124, 126, 128) de telle sorte que, en utilisation de l'ensemble formant pompe (102), du carburant est forcé hors de la chambre (158) vers un trajet de fuite en retour, via ledit au moins un palier (140, 142, 144) et la surface à palier lisse (124, 126, 128),
    dans lequel la chambre (158) est en communication fluidique avec un palier arrière (142) et une surface à palier lisse arrière (128) sur laquelle le palier arrière (142) est situé ;
    et dans lequel la chambre (158) est également en communication fluidique, via des perçages (134, 136, 138) prévus dans l'arbre d'entraînement (106), avec un palier avant (140) et une surface à palier lisse avant (126) de la portion à palier lisse avant (120) sur laquelle le palier avant (140) est situé, et/ou avec un palier de coiffe (144) et une surface à palier lisse de coiffe (124) de la portion en came (110) sur laquelle le palier de coiffe (144) est situé,
    dans lequel les perçages (134, 136, 138) prévus dans l'arbre d'entraînement (106) comprennent un perçage axial (134), un premier perçage radial (136) prévu dans la portion en came (110), et un second perçage radial (138) prévu dans la portion à palier lisse avant (120) ;
    dans lequel le perçage axial (134) fait communiquer le premier perçage radial (136) et le second perçage radial (138) avec la chambre (158) ;
    le premier perçage radial (136) fait communiquer le perçage axial (134) avec le palier de coiffe (144) et la surface à palier lisse de coiffe (124) ;
    et le second perçage radial (138) fait communiquer le perçage axial (134) avec le palier avant (140) et la surface à palier lisse avant (126),
    dans lequel le carburant qui s'écoule hors de la chambre (158) via le palier arrière (142) et la surface à palier lisse arrière (128), et via le palier de coiffe (144) et la surface à palier lisse de coiffe (124), s'écoule en entrant dans un volume (118) à l'intérieur de la boîte à came (108), et dans lequel le carburant qui s'écoule hors de la chambre (158) via le palier avant (140) et la surface à palier lisse avant (126) s'écoule soit en entrant dans le volume (188) à l'intérieur de la boîte à came (108) soit en entrant dans une galerie annulaire (180) prévue à l'intérieur du boîtier de pompe (104) autour de l'arbre d'entraînement (106) ;
    et dans lequel le trajet de fuite de retour comprend :
    une première section de trajet sortant (190) permettant une communication fluidique sans restriction entre le volume (118) à l'intérieur de la boîte à came (108) et une section commune du trajet de fuite de retour (194) ;
    caractérisé en ce qu'il est prévu une seconde section de trajet sortant (192), permettant une communication fluidique entre la galerie (180) et la section commune du trajet de fuite de retour (194),
    dans lequel la seconde section de trajet sortant (192) est constituée par un perçage ayant une surface de section transversale plus petite qu'une surface de section transversale de la première section de trajet (190).
  2. Ensemble formant pompe (102) selon l'une quelconque des revendications précédentes, comprenant en outre au moins un canal (160, 162) prévu dans le boîtier de pompe (104) et menant depuis la chambre (158) jusqu'à la boîte à came (108).
  3. Ensemble formant pompe (102) selon la revendication 2, dans lequel un étranglement (170, 172), comprenant une section de canal ayant une surface de section transversale réduite est prévu dans le ou dans chaque canal (160, 162).
EP16157228.4A 2015-03-25 2016-02-24 Ensemble de pompe Active EP3073110B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GBGB1504999.2A GB201504999D0 (en) 2015-03-25 2015-03-25 Pump assembly

Publications (2)

Publication Number Publication Date
EP3073110A1 EP3073110A1 (fr) 2016-09-28
EP3073110B1 true EP3073110B1 (fr) 2018-04-18

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP16157228.4A Active EP3073110B1 (fr) 2015-03-25 2016-02-24 Ensemble de pompe

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Country Link
EP (1) EP3073110B1 (fr)
GB (1) GB201504999D0 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2554845A (en) * 2016-05-17 2018-04-18 Delphi Int Operations Luxembourg Sarl Fuel pump
GB2556078B (en) * 2016-11-17 2020-02-26 Delphi Tech Ip Ltd Venturi flow circuit

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2628232B1 (de) * 1976-06-23 1977-11-10 Langen & Co Hydraulische radialkolbenpumpe
DE19953248A1 (de) * 1999-11-04 2001-05-23 Luk Fahrzeug Hydraulik Radialkolbenpumpe
JP2003172230A (ja) * 2001-12-03 2003-06-20 Nachi Fujikoshi Corp 高圧プランジャポンプの強制潤滑装置
DE102011082729A1 (de) * 2011-09-15 2013-03-21 Robert Bosch Gmbh Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem sowie Pumpenanordnung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
GB201504999D0 (en) 2015-05-06
EP3073110A1 (fr) 2016-09-28

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