EP2872771A1 - Pompe haute pression - Google Patents

Pompe haute pression

Info

Publication number
EP2872771A1
EP2872771A1 EP13733272.2A EP13733272A EP2872771A1 EP 2872771 A1 EP2872771 A1 EP 2872771A1 EP 13733272 A EP13733272 A EP 13733272A EP 2872771 A1 EP2872771 A1 EP 2872771A1
Authority
EP
European Patent Office
Prior art keywords
channel
housing
drive shaft
pressure pump
fuel
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
EP13733272.2A
Other languages
German (de)
English (en)
Other versions
EP2872771B1 (fr
Inventor
Achim Koehler
Armin Merz
Sandro Soccol
Joerg Morlok
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2872771A1 publication Critical patent/EP2872771A1/fr
Application granted granted Critical
Publication of EP2872771B1 publication Critical patent/EP2872771B1/fr
Not-in-force 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil

Definitions

  • the present invention relates to a high-pressure pump according to the preamble of claim 1 and a high-pressure injection system according to the preamble of claim 10.
  • a high-pressure pump permanently ensures the maintenance of the pressure in the
  • High pressure accumulator of the common rail injection system can be driven, for example, by a camshaft of the internal combustion engine by means of a drive shaft.
  • Rotary vane pump used, which are upstream of the high-pressure pump.
  • the prefeed pump delivers the fuel from a fuel tank through a fuel line to the high pressure pump.
  • piston pumps are used as high-pressure pumps.
  • a drive shaft is mounted. Radially to pistons are arranged in a cylinder.
  • a roller with a roller rolling surface On the drive shaft with at least one cam is a roller with a roller rolling surface, which is mounted in a roller shoe.
  • the roller shoe is connected to the piston, so that the piston is forced to oscillate translational motion.
  • a spring applies to the roller shoe a radially directed to the drive shaft force, so that the roller is in constant contact with the drive shaft.
  • the roller is available the roller rolling surface on a shaft rolling surface as the surface of the drive shaft with the at least one cam in contact with the drive shaft.
  • the roller is mounted by means of a sliding bearing in the roller shoe.
  • the high-pressure pump has a lubricant space formed within a housing and within the lubricant space the drive shaft with the cams, the roller shoe and the roller is arranged.
  • the lubricating space is traversed by fuel as a lubricating fluid for lubrication and cooling of the components, d. H. in particular the roller, the roller shoe and the drive shaft as well as the piston, which is slidably mounted on a piston guide on the housing.
  • the funded by the feed pump fuel is thereby part of the high-pressure pump, d. H. one
  • the housing includes an opening for passage and sliding bearing of
  • the drive shaft and a blind hole for mounting the drive shaft.
  • the drive shaft is slidably mounted on the blind hole and the opening by means of a bearing bush.
  • This fuel which due to the clearance between the drive shaft and the bearing bush axially flows through this gap or gap, in particular annular gap, is thereby after flowing through a
  • DE 10 2006 045 933 A1 shows a high pressure pump for high pressure fuel delivery.
  • the high-pressure pump has a drive shaft with cams. Cylindrical rollers are supported by roller shoes and rest on the cams. The roller shoes are mounted by means of a plunger assembly in a bore of a part of the housing.
  • the pump elements are at the
  • Inventive high-pressure pump for conveying a fluid, in particular fuel, for. B. diesel, comprising a housing, a drive shaft with at least one cam, at least one piston, at least one cylinder for supporting the at least one piston, wherein the at least one piston indirectly, in particular by means of at least one roller or a bucket tappet, on the drive shaft the at least one cam is supported, so that from the at least one piston a translational movement due to a rotational movement of the drive shaft is executable, a lubricating space within which the drive shaft is arranged with the at least one cam, for lubrication and cooling of the drive shaft, at least one shaft sliding bearing for storage the drive shaft with a fluid-conducting
  • Lubrication chamber is lubricated and cooled, wherein in the housing and / or a bearing bush for the drive shaft at least one channel is incorporated for the additional discharge of lubricating fluid from the lubricant space.
  • the housing and / or the bearing bush for the drive shaft at least one channel is incorporated, thereby additionally in addition to the gap, in particular annular gap, due to a game between the drive shaft and the journal bearings fuel can be derived from the lubricating space in order to perform a sufficient cooling of the components within the lubricating space can.
  • no additional or additional cooling throttle is required as a separate component on the high pressure pump on the lubricating space in an advantageous manner.
  • an opening in the housing which is exclusively bounded by the housing, is not considered to be the channel.
  • the high-pressure pump does not comprise a cooling throttle as a separate component and, in particular, exclusively for this purpose.
  • the at least one channel can thus be additionally derived with existing components of the fuel from the lubricating space by the channel is incorporated into the housing and / or the bearing bush and thus no additional components are required.
  • the at least one channel is formed as a groove in the housing and / or the bearing bush and / or the housing has a
  • Opening and / or a blind hole for storage of the drive shaft and the at least one channel is formed on the opening and / or the blind hole and / or the housing comprises a hull housing and a bearing cover housing.
  • Bearing bush incorporated by embossing and / or milling and / or by means of a laser.
  • the at least one channel can be integrated into existing components.
  • the at least one groove is formed on a radial outer side of the bearing bush.
  • the groove is V-shaped in cross-section
  • the at least one channel opens into a return bore and / or a return line.
  • the derived by the at least one channel lubricating fluid, in particular fuel, is after deriving from the channel through the return line and / or the
  • the at least one incorporated into the housing channel of the housing and the bearing bush is limited, since the at least one in the
  • Housing incorporated channel is incorporated in the region of a bearing surface of the bearing bush on the housing.
  • the at least one channel is thus formed between the housing and the bearing bush.
  • the shaft sliding bearing is formed for example by the housing or the bearing bush.
  • the high-pressure pump expediently comprises at least two or three channels, in particular per shaft sliding bearing for the drive shaft, and / or at least one channel opens into an annular channel and preferably the annular channel opens into a return bore and / or a return line.
  • the at least one channel is aligned parallel or at an acute angle to a rotational axis of the drive shaft.
  • the acute angle is between 1 ° and 45 °, in particular between 1 ° and 30 °.
  • the annular channel is incorporated in an analogous manner as the at least one channel in the housing and / or the bearing bush.
  • the gap in particular annular gap, between the
  • connection and in particular the return restriction throttle in an analogous manner as the at least one channel is incorporated in the housing and / or the bearing bush.
  • the return restriction restrictor serves to cause the leakage between the shaft sliding bearing and the drive shaft due to play
  • the return restrictor is incorporated in an analogous manner as the at least one channel in the housing and / or bearing bush for the drive shaft, ie, for example, as a groove on a radial outer side of the bearing bush.
  • a high-pressure injection system for an internal combustion engine comprising a high-pressure pump having a lubrication space, a high-pressure rail, a demand pump for supplying a fuel from a fuel tank to the high-pressure pump, the high-pressure pump being one of them
  • Patent application described high-pressure pump is formed.
  • the high-pressure injection system in particular the high-pressure pump, comprises a pressure sensor for detecting the pressure in the lubricant space.
  • the delivery rate of the forecasting pump in particular as a function of the pressure detected by the pressure sensor in the lubricant chamber and / or as a function of the volume flow of fuel required by the internal combustion engine, can be controlled and / or regulated.
  • the delivery rate of the precharge pump is controlled and / or regulated to the effect that on the one hand there is sufficient fuel for the internal combustion engine, ie a sufficient volume flow of fuel is supplied to the inlet channel of the high-pressure pump and on the other hand enough fuel flows through the lubricant space for lubrication and / or cooling as the second Volume flow and this second volume flow is dependent on the pressure within the lubricating space.
  • the pre-demand pump is a pre-demand pump with electric motor, so that the pre-demand pump is driven by the electric motor and in particular the delivery rate of the pre-demand pump can be controlled and / or regulated.
  • the drive shaft with the at least one cam is expediently a drive shaft which is circular in cross-section and which is mounted eccentrically to a central longitudinal axis of the drive shaft so that the axis of rotation is at a distance from the longitudinal axis.
  • the longitudinal axis is arranged in cross section in the center of the circular drive shaft.
  • the Vorforderpumpe is a gear or rotary vane pump.
  • FIG. 1 shows a cross section of a high-pressure pump for conveying a fluid
  • FIG. 2 shows a section A-A of FIG. 1 a roller with roller shoe and a drive shaft
  • FIG. 3 is a highly schematic view of a high-pressure injection system
  • Fig. 4 is a greatly simplified cross-section of the high pressure pump
  • FIG. 5 shows a section of the housing of the high-pressure pump with an opening and a blind hole for mounting the drive shaft
  • Fig. 6 is a longitudinal section of a sliding bearing at the opening with
  • Fig. 7 is a longitudinal section of the sliding bearing on the blind hole with the bearing bush
  • Fig. 14 shows a first embodiment of the at least one channel
  • Fig. 15 shows a second embodiment of the at least one channel
  • Fig. 18 is a partial cross section of the bearing bush with a cross-section
  • Fig. 1 is a cross section of a high-pressure pump 1 for conveying fuel is shown.
  • the high-pressure pump 1 serves to fuel, z.
  • the pressure which can be generated by the high-pressure pump 1 is, for example, in a range between 1000 and 3000 bar.
  • the high-pressure pump 1 has a drive shaft 2 with two cams 3, which performs a rotational movement about a rotation axis 26.
  • a piston 5 is mounted in a cylinder 6 which is formed by a housing 8 of the high-pressure pump 1.
  • a high pressure working chamber 29 is bounded by the cylinder 6 as a piston guide 7, the housing 8 and the piston 5.
  • Into the high-pressure working space 29 opens an inlet channel 22 with an inlet valve 19 and an outlet channel 24 with an outlet valve 20.
  • the fuel flows into the high-pressure working chamber 29 and through the outlet channel 24 with an outlet opening 23, the fuel flows under High pressure from the
  • Working space 29 can flow and the exhaust valve 20, z. B. a
  • Check valve is designed so that only fuel can flow out of the working chamber 29.
  • the volume of the high-pressure working chamber 29 is changed due to an oscillating stroke movement of the piston 5.
  • Piston 5 is indirectly supported on the drive shaft 2 from. At the end of the piston 5 or pump piston 5, a roller shoe 9 is attached to a roller 10. The roller 10 can perform a rotational movement, the
  • Rotation axis 25 lies in the plane of FIG. 1 and is perpendicular to the plane of Fig. 2.
  • Cam 3 has a shaft rolling surface 4 and the roller 10 has a roller rolling surface 1 1.
  • roller tread 1 1 of the roller 10 rolls on the shaft rolling surface 4 as a contact surface 12 of the drive shaft 2 with the two cams 3 from.
  • Roller shoe 9 is mounted in a roller shoe bearing formed by the housing 8 as a sliding bearing.
  • a spring 27 or coil spring 27 as an elastic element 28 which is clamped between the housing 8 and the roller shoe 9, brings on the roller shoe 9 a compressive force, so that the roller rolling surface 1 1 of the roller 10 in constant contact with the waves Rolling surface 4 of the drive shaft 2 is.
  • the roller shoe 9 and the piston 5 lead with it together an oscillating stroke movement.
  • the roller 10 is mounted with a sliding bearing 13 in the roller shoe 9.
  • Fig. 3 is a highly schematic representation of a high-pressure injection system 36 for the motor vehicle shown with a high-pressure rail 30 or a
  • Fuel rail 31 From the high-pressure rail 30 and a
  • An electric pre-demand pump 35 delivers fuel from a fuel tank 32 through a first fuel line 33a to the intake passage 22 and through a second fuel line 33b to a lubricating space 40 (FIG. 4)
  • High pressure pump 1 The high pressure pump 1 is driven by the drive shaft 2 and the drive shaft 2 is connected to a shaft, for. As a crankshaft or camshaft, the engine 39 is connected.
  • the delivery rate of the electric pre-charging pump 35 is controllable and / or controllable, so that thereby the amount of fuel delivered to the inlet channel 22 per
  • Time unit can be controlled and / or regulated.
  • the high-pressure rail 30 serves to inject the fuel into the combustion chamber of the internal combustion engine 39.
  • the fuel which is not required by the high-pressure pump 1 is thereby returned to the system through an optional fuel return line 34
  • Fuel tank 32 returned.
  • Fig. 4 shows a part of the high-pressure injection system 36.
  • Fuel tank 32 fed back ( Figure 4).
  • the high pressure injection system 36 shown in FIG. 3 is shown in more detail without the high pressure rail 30 and without the engine 39.
  • the sucked by the Vorforderpumpe 35 from the fuel tank 32 fuel is supplied by the Vorforderpumpe 35 with a prefeed, z. B. 4 bar, through the first fuel line 33 a the
  • Inlet passage 22 of the high pressure pump 1 is supplied. Furthermore, the of the Pre-feed pump 35 pumped fuel during operation of the
  • the prefeed pump 35 thereby promotes in addition to the flow rate for the high-pressure pump 1 of fuel and an additional amount of fuel for lubrication of the high-pressure pump 1, d. H. of the fuel flowing through the lubricating space 40.
  • the electric prefeed pump 35 has an electric motor 17 and a
  • Rotary piston pump 16 namely a gear pump 14, d. H. a
  • High-pressure pump 1 delivers fuel under high pressure, for example one
  • Pre-feed pump 35 is operated with three-phase or alternating current and is controllable in performance and / or adjustable.
  • the three-phase current or alternating current for the electric motor 17 is provided by a power electronics, not shown, from a DC voltage network of a vehicle electrical system of a motor vehicle (not shown).
  • the electric prefeed pump 35 is thus an electronically commutated prefeed pump 35.
  • the housing 8 of the high-pressure pump 1 is subdivided into a hull housing 46 and into a bearing cover housing 47 as separate components (FIGS. 4 and 5).
  • the hull housing 46 is formed with a blind hole 45 and the
  • Bearing housing 47 or flange housing 47 has an opening 44
  • the opening 44 serves to form a shaft sliding bearing 18 for the drive shaft 2 and also for the implementation of the drive shaft 2 outside the lubricating space 40, so that thereby the drive shaft 2 can be mechanically connected, for example, with a camshaft, not shown, of the engine 39.
  • the blind hole 45 only serves to provide a shaft sliding bearing 18 for the drive shaft 2 available.
  • a bearing bush 41 by means of a press fit on a bearing surface 49 on the housing 8, ie the hull housing 46 and the bearing cap housing 47, on or pressed.
  • the bearing bush 41 thus forms on its radial inside the shaft sliding bearing 18 on which the drive shaft 2 rests.
  • Gap 37 flows under a pressure of, for example, 4 to 5 bar standing fuel within the lubricant chamber 40 in the axial direction to an axial end of the shaft sliding bearing 18.
  • a drain hole 52 is also present. The fuel flowing through the gap 37 between the drive shaft 2 and the bearing bush 41 is thus collected at the drainage bore 52 and then fed back to the fuel tank 32 through the fuel return line 34 shown in FIG.
  • a shaft seal not shown, is present and further sealing means, for. B.
  • Return restrictor 51 collected a return bore 48 is supplied. To the return bore 48 is in an analogous manner as at
  • the drainage hole 52 is as a
  • Return limitation throttle 51 is formed. After flowing through the return restriction throttle 51 between the bearing bush 41 and the
  • bearing housing 47 this fuel of the return bore 48 is supplied due to a corresponding fluid-conducting connection and the incorporated in the bearing cap housing 47 return bore 48 is fluidly connected to the fuel return line 34.
  • a groove 43 (Fig. 6) is incorporated on the radially outer side by means of embossing, pressing or milling.
  • the bearing bush 41 is fixed by means of a press fit to the opening 44 of the bearing cap housing 47, ie on the support surface 49. The rotational position of the bearing bush 41 with respect to
  • Bearing housing 47 is fixed, so that on the one hand due to the groove 43, a channel 42 between the bearing cap housing 47 and the bearing bush 41 is formed and this channel 42 and hydraulically with the
  • Return bore 48 opens. Thus open into the return bore 48, both the channel 42 and the return restriction throttle 51. Die
  • Return restrictor 51 is similar to the channel 42 in the radial outer side of the bearing bush 41 by means of pressing or embossing
  • the fuel flowing out through the channel 42 is thus also supplied to the fuel return line 34 through the return bore 48.
  • the bearing book 41 on the blind hole 45 also on the outside a groove 43 (Fig. 7) and thereby forms between the bearing bush 41 and the body shell 46 also the channel 42.
  • This channel 42 can be additionally derived fuel, which through the drain hole 52 also the fuel return line 34 and thus the fuel tank 32 is supplied.
  • the flow cross-sectional area of the drainage bore 52 may optionally also be designed such that the drainage bore 52 also serves as a return restriction throttle 51.
  • the fuel delivered by the prefeed pump 35 is supplied on the one hand through the first fuel line 33a to the inlet channel 22 and through the second fuel line 33b the lubricating chamber 40.
  • the lubricating chamber 40 is completely filled with fuel and the fuel is used for lubrication
  • Components e.g. B. the drive shaft 2 and the roller shoe 9, and also for cooling these components.
  • a sufficient volume flow of fuel must be passed through the lubricating space 40.
  • the two channels 42 which are incorporated on the radial outer side of the two bushings 41 in the form of grooves 43, in addition fuel from the
  • Lubrication chamber 40 are derived.
  • this channel 42 is a cooling throttle without additional components to the high-pressure pump 1, because the channel 42 is integrated into existing components, namely by the groove 43 is incorporated into the bearing bush 41 on the outside.
  • Figs. 8 to 13 are views of the bearing bush 41 in different
  • Bearing bush 41 only a channel 42 and a groove 43 which is aligned parallel to a rotation axis 26 of the drive shaft 2.
  • the bearing bush 41 has two grooves 43 and in the embodiment shown in Fig. 10, the grooves 43 are incorporated at an acute angle to the axis of rotation 26.
  • the embodiment shown in Fig. 1 1 differs from the embodiment shown in Fig. 10 in that the two grooves 43 are interconnected by an additional groove and in Fig. 12, the two grooves 43 are also connected to each other by an additional groove, but parallel to the
  • Embodiment open two grooves 43 in the lubricating space 40 and these two grooves 43 then open into only one groove 43.
  • FIGS. 14 and 15 are two embodiments of the embodiment of
  • Bearing bush 41 in addition to at least one groove 43 also shown in addition to an annular channel 50.
  • the embodiment shown in Fig. 14 corresponds to the embodiment shown in Fig. 8 and differs only in that an annular channel 50 is present. In an analogous way
  • FIG. 15 differs from that in FIG.
  • FIGS. 10 to 13 illustrated embodiment only in that an annular channel 50 is present.
  • the exemplary embodiments illustrated in FIGS. 10 to 13 can also be provided with an annular channel 50.
  • Ring channel 50 is the bearing bush 41 in the opening 44 is not in his
  • the cross-sectional shape of the groove 43 incorporated in the bearing bushing 41 is arbitrary and may, for example, be V-shaped (FIG. 16), rectangular (FIG. 17) or circular segment-shaped (FIG. 18).
  • the groove 43 is not on the radial outer side of the bearing bush 41, but on the radial inner side of the bearing bush 41, d. H. formed on the shaft sliding bearing 48.
  • the channel 42 is thereby bounded by the bearing bush 41 or the shaft sliding bearing 18 and the drive shaft 2. This can additionally fuel from the
  • Lubrication chamber 40 are derived.
  • the return flow restrictor 51 and the return bore 48 are formed at the blind hole 45 as in the embodiment in Fig. 6 at the opening 44 and the housing 8, d. H. the hull housing 46 has no drainage bore 52 on the blind hole 45.
  • a pressure sensor 53 is present in the lubricating space 40.
  • the pressure sensor 53 detects the pressure of the fuel within the lubricating space 40, which is for example in the range of 4 to 5 bar.
  • Pre-feed pump 35 is controllable and / or regulated and is thereby controlled and / or regulated so that in the lubricating chamber 40, a constant pressure of 4 to 5 bar is present.
  • the pressure in the lubricating space 40 can also be increased in order to discharge an increased amount of fuel from the lubricating space 40 by increasing the pressure in order to increase the pressure
  • the high-pressure pump 1 does not have a separate cooling throttle for the additional discharge of fuel from the lubricating space 40 on, so that thereby the manufacturing cost of the high-pressure pump 1 can be lowered.
  • a groove 43 is incorporated, thereby forming a channel 42 as a cooling throttle for the additional discharge of fuel from the lubricating space 40.

Landscapes

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

Abstract

L'invention concerne une pompe haute pression (1) servant à alimenter un fluide, en particulier du carburant, par exemple du gazole, comprenant un carter (8), un arbre d'entraînement (2) portant au moins une came (3), au moins un piston (5), au moins un cylindre (6) destiné à recevoir le piston (5), le ou les pistons (5) s'appuyant indirectement sur l'arbre d'entraînement (2) par le biais d'au moins une came (3) de telle sorte que le ou les pistons (5) peuvent effectuer un mouvement de translation suite à un mouvement de rotation de l'arbre d'entraînement (2), un espace de graissage (40), à l'intérieur duquel l'arbre d'entraînement (2) portant la ou les cames (3) est disposé, servant à graisser et refroidir l'arbre d'entraînement (2), au moins un palier lisse d'arbre destiné à supporter l'arbre d'entraînement avec une liaison fluidiquement conductrice d'une fente, en particulier une fente annulaire, entre le palier lisse et l'arbre d'entraînement (2) jusqu'à l'espace de graissage (40), de telle sorte qu'au moins un palier lisse d'arbre est graissé et refroidi avec le liquide de graissage provenant de l'espace de graissage (40). Dans le carter (8) et/ou dans un coussinet (41) de l'arbre d'entraînement (2), au moins un conduit est usiné pour former une dérivation supplémentaire pour le liquide de graissage à partir de l'espace de graissage (40).
EP13733272.2A 2012-07-11 2013-06-27 Pompe haute pression Not-in-force EP2872771B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201210212153 DE102012212153A1 (de) 2012-07-11 2012-07-11 Hochdruckpumpe
PCT/EP2013/063468 WO2014009164A1 (fr) 2012-07-11 2013-06-27 Pompe haute pression

Publications (2)

Publication Number Publication Date
EP2872771A1 true EP2872771A1 (fr) 2015-05-20
EP2872771B1 EP2872771B1 (fr) 2017-01-04

Family

ID=48745927

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13733272.2A Not-in-force EP2872771B1 (fr) 2012-07-11 2013-06-27 Pompe haute pression

Country Status (5)

Country Link
EP (1) EP2872771B1 (fr)
CN (1) CN104487699B (fr)
DE (1) DE102012212153A1 (fr)
IN (1) IN2014DN10747A (fr)
WO (1) WO2014009164A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3411588B1 (fr) * 2016-02-02 2019-11-27 Wärtsilä Finland Oy Système de palier
DE102018120777A1 (de) * 2018-08-24 2020-02-27 Volkswagen Aktiengesellschaft Hochdruckpumpe umfassend eine Druckumlaufschmierung

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1172014A (ja) * 1997-06-24 1999-03-16 Unisia Jecs Corp 燃料加圧用ポンプ
DE19924064B4 (de) * 1999-05-26 2007-07-05 Siemens Ag Verdrängerpumpe
JP3852753B2 (ja) * 2001-12-04 2006-12-06 株式会社デンソー 燃料噴射ポンプ
JP3915718B2 (ja) * 2003-03-11 2007-05-16 株式会社デンソー 燃料供給ポンプ
DE10356262A1 (de) * 2003-12-03 2005-06-30 Robert Bosch Gmbh Radialkolbenpumpe, insbesondere für Kraftstoffeinspritzsysteme
DE102006045933A1 (de) 2006-09-28 2008-04-03 Robert Bosch Gmbh Stößelbaugruppe für eine Hochdruckpumpe und Hochdruckpumpe mit wenigstens einer Stößelbaugruppe
JP4701227B2 (ja) * 2007-10-29 2011-06-15 日立オートモティブシステムズ株式会社 プランジャ式高圧燃料ポンプ
DE102008017222A1 (de) * 2008-04-04 2009-10-08 Continental Automotive Gmbh Pumpenanordnung zur Förderung eines Fluids

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2014009164A1 *

Also Published As

Publication number Publication date
WO2014009164A1 (fr) 2014-01-16
CN104487699A (zh) 2015-04-01
IN2014DN10747A (fr) 2015-09-04
DE102012212153A1 (de) 2014-01-16
EP2872771B1 (fr) 2017-01-04
CN104487699B (zh) 2018-03-13

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