WO2019081239A1 - Compresseur à piston - Google Patents

Compresseur à piston

Info

Publication number
WO2019081239A1
WO2019081239A1 PCT/EP2018/077973 EP2018077973W WO2019081239A1 WO 2019081239 A1 WO2019081239 A1 WO 2019081239A1 EP 2018077973 W EP2018077973 W EP 2018077973W WO 2019081239 A1 WO2019081239 A1 WO 2019081239A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
piston
leckageminimierungshülse
sleeve
pressure
Prior art date
Application number
PCT/EP2018/077973
Other languages
German (de)
English (en)
Inventor
Dietmar Uhlmann
Dirk SCHNITTGER
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 WO2019081239A1 publication Critical patent/WO2019081239A1/fr

Links

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
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • 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
    • 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
    • F04B1/0443—Draining of the housing; Arrangements for handling leaked fluids
    • 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
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/20—Other positive-displacement pumps
    • F04B19/24—Pumping by heat expansion of pumped fluid
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/045—Labyrinth-sealing between piston and cylinder
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/122—Cylinder block
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/126—Cylinder liners
    • 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
    • F04B53/008—Spacing or clearance between cylinder and piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/166—Cylinder liners
    • 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
    • F02M2200/26—Fuel-injection apparatus with elastically deformable elements other than coil springs

Definitions

  • Piston compressor The invention relates to a piston compressor for compressing a working fluid having the features of the preamble of claim 1.
  • the working fluid can in particular be a liquid or leakage-minimizing sleeve fuel, such as natural gas ("NG").
  • natural gas such as natural gas
  • NG natural gas
  • LNG liquid form
  • the proposed reciprocating compressor can be used for compressing any gaseous and / or liquid media, so that the presently selected term "piston compressor” also includes piston pumps
  • a piston compressor for the compression of a cooling gas emerges, which comprises a cylinder and a reciprocating piston in the cylinder.
  • the cylinder and piston define a compression chamber.
  • the piston is connected to a drive mechanism, wherein the
  • the present invention has for its object to provide a reciprocating compressor, which has an improved efficiency. To achieve this, the leakage in the region of an annular gap between the piston and the cylinder of the reciprocating compressor should be minimized.
  • the reciprocating compressor should in this way also be suitable for compressing a liquid or gaseous fuel, such as natural gas, to high pressure (preferably about 600 bar).
  • the piston compressor proposed for compressing a working fluid comprises a piston which can be moved back and forth in a bore of a cylinder and which delimits within the bore a compression space which can be filled with the working fluid.
  • a working fluid in particular a liquid or gaseous fuel
  • an encircling annular groove is formed on the inner circumference in the cylinder, in which a leakage minimizing sleeve is accommodated, which together with the cylinder defines an annular pressure chamber which is hydraulically connected to the compression space.
  • the pressure in the pressure chamber is therefore the same as in the compression chamber.
  • the stroke of the piston causes compression of the trapped working fluid in the compression space. This means that the pressure in the compression chamber increases. At the same time, the pressure in the pressure chamber hydraulically connected to the pressure chamber increases. Since the pressure on the outside of the leakage minimizing sleeve is greater than the inside, the sleeve contracts, causing the gap remaining between the piston and the leakage minimizing sleeve to decrease. As the gap is reduced, the leakage across the gap also decreases. so that in this way an increase in the efficiency of the reciprocating compressor is achieved.
  • the contraction of the leakage minimization sleeve is proportional to the pressure increase in the compression chamber or in the pressure chamber. This means that as the pressure increases, so does the contraction. This is due to the constant pressure in the longitudinal direction in the pressure chamber, while in the gap between the Leckageminimtechnikshülse and the piston in the longitudinal direction sets an (approximately) linear pressure drop. The desired effect of gap minimization is thus given over the entire pressure range.
  • the contraction of the leakage minimization sleeve is further facilitated by the fact that the inner peripheral surface is smaller than the outer peripheral surface of the sleeve, so that radially outward on the leakage minimization sleeve already due to the larger area a larger pressure force acts.
  • the leakage minimization sleeve is to be distinguished from a conventional sealing sleeve. Because through the sleeve no seal, but only a gap minimization is achieved. This means that a certain flow is maintained in the gap. In this way, friction losses can be minimized.
  • the inner diameter of the Leckageminim istshülse is chosen over the entire length greater than the outer diameter of the piston, so that wear and clamps are reduced to a minimum.
  • the leakage minimization sleeve allows compensation of any production-related diameter tolerances, so that at the same time the production of the reciprocating compressor is simplified.
  • the annular groove is arranged at least in sections at the level of the piston on the inside of the cylinder in order to achieve the desired minimization of leakage by minimizing the gap between the piston and the leakage minimization sleeve accommodated in the annular groove.
  • the annular groove has a height Hi which is greater than a height H2 of the leakage minimizing sleeve. This means that an axial gap remains between the leakage minimization sleeve and the cylinder, via which the required hydraulic connection of the pressure chamber with the compression space can be established.
  • the leakage minimizing sleeve preferably bears sealingly against the cylinder, so that circumvention of the leakage minimization sleeve is precluded.
  • a spring element be received in the annular groove, by means of which the leakage minimizing sleeve is axially biased against the cylinder. Due to the axial bias, the leakage minimizing sleeve is fixed in position in the axial direction, so that circumvention of the leakage minimization sleeve is permanently excluded.
  • the biasing force also serves as an initial sealing force in the axial direction.
  • the spring element is supported on an end face of the leakage minimizing sleeve.
  • a spring element for example, a helical compression spring, a wave spring or a plate spring can be used which is inserted into the annular groove, and preferably in the remaining between the leakage minimization sleeve and the cylinder axial gap.
  • the specific design of the spring element is to ensure that the required hydraulic connection of the pressure chamber is not interrupted or impaired with the compression space.
  • the spring element may be formed as a double collar sleeve having a radially outwardly projecting first collar for axial support on the cylinder and a radially inwardly projecting second collar for axial support on the Leckageminim réelleshülse.
  • the leakage minimization sleeve is also fixed in its axial position.
  • the second collar of the collar bush is designed in the manner of a spring arm and rests only on an annular contour on the end face of the Leckageminim réelleshülse. The axial pretensioning force can then be applied by way of the spring-arm-shaped second collar.
  • the leakage minimization sleeve for support on the cylinder has a frontally arranged, substantially planar annular contact surface, which is adjoined radially inwardly by a cone. Via the cone, the footprint is reduced, which is thus smaller than the end face at the other end of the Leckageminim istshülse. By reducing the footprint an improved sealing effect can be achieved.
  • the cone in the radial direction has a width b which is greater than a width a of the contact surface, so that the contact surface is significantly reduced.
  • the ratio of the width a to the width b is preferably 3: 1. In this way, a defined local footprint is created.
  • the area opposite the footprint of the leakage minimizing sleeve may be formed on the cylinder such that the contact area between the leakage minimizing sleeve and the cylinder is reduced.
  • the end face of the leakage minimizing sleeve can also be made flat.
  • the pressure applied to the end face of the leakage minimization sleeve facing the compression space leads to a hydraulic pressure force which presses the leakage minimization sleeve against the cylinder. Since no compression space pressure is applied to the other end face of the leakage minimizing sleeve, at least in the area radially inside the contact area with the cylinder or the contact area, the leakage minimization sleeve is held in contact with the cylinder in this manner. Due to the force difference existing in the axial direction, a spring element for axial prestressing of the leakage minimizing sleeve may possibly be dispensed with altogether.
  • the cylinder is designed in several parts and comprises at least one upper part and a lower part, which are preferably placed axially against each other in the region of the annular groove.
  • the multi-part design facilitates the production of the annular groove, in particular, when the annular groove in only one part, preferably in the upper part, must be formed.
  • the annular groove can be formed as an open-sided groove, which is closed by the attachment of the further part, preferably of the lower part, in the axial direction. Before joining the two parts, the spring element and the leakage minimizing sleeve are inserted into the annular groove.
  • the multi-part design of the cylinder thus simplifies the assembly of the reciprocating compressor.
  • the compression space can be connected via an inlet valve to a fluid supply and / or via an outlet valve to a pressure line.
  • the working fluid enters the compression chamber via the inlet valve, where it is compressed by means of the piston stroke.
  • the compressed working fluid can then be fed via the outlet valve and the subsequent pressure line to a fluid reservoir, which is preferably a high-pressure accumulator for a liquid or gaseous fuel, such as natural gas, which is injected under high pressure into the combustion chamber of an internal combustion engine.
  • a fluid reservoir which is preferably a high-pressure accumulator for a liquid or gaseous fuel, such as natural gas, which is injected under high pressure into the combustion chamber of an internal combustion engine.
  • FIG. 1 is a schematic sectional view of a piston compressor according to the invention according to a first preferred embodiment
  • FIG. 2 shows an enlarged detail of FIG. 1 in the region of the annular groove formed in the cylinder
  • FIG. 3 is an enlarged detail of FIG. 2 in the region of the support of the spring element on the leakage minimizing sleeve, FIG.
  • FIG. 4 shows an enlarged detail of FIG. 2 in the region of the support of the leakage minimization sleeve on the cylinder
  • 5 shows a schematic longitudinal section through a piston compressor according to the invention according to a second preferred embodiment (limited to the region of the annular groove)
  • 6 shows a schematic longitudinal section through an inventive piston compressor according to a third preferred embodiment (limited to the region of the annular groove) and
  • Fig. 7 is a schematic longitudinal section through a piston compressor according to the invention according to a fourth preferred embodiment.
  • the piston compressor 1 according to the invention shown in FIG. 1 comprises a cylinder 3 with a bore 2, in which a piston 4 is reciprocally accommodated (see arrow 20).
  • the piston 4 bounded within the bore 2 a compression chamber 5, which is connectable via an inlet valve 16 to a fluid supply 17 or filled with a working medium.
  • a fluid reservoir (not shown) may be connected to the pressure line 13 to the pressure line 13.
  • the cylinder 3 In order to reduce the leakage from the compression chamber 5 via an annular gap 24 which remains between the piston 4 and the cylinder 3, the cylinder 3 at the level of the piston 4 on the inner circumference a circumferential annular groove 6, in which a Leckageminim istshülse 7 is received ,
  • the leakage minimization sleeve 7 delimits with the cylinder 3 an annular pressure chamber 8, which is hydraulically connected to the compression space 5, so that radially outward against the leakage minimization sleeve 7 the same pressure as in the compression space 5 is applied.
  • the pressure At a pressure increase in the compression chamber 5, the pressure also increases radially on the outside of the leakage minimization sleeve 7, which then contracts and seals against the piston 4.
  • the annular pressure chamber 8 is filled via the annular gap 24 with working fluid (see arrow 22).
  • the pressure in the compression chamber and at the same time the pressure in the pressure chamber 8 increase.
  • the sealing effect is enhanced by the fact that the leakage minimizing sleeve 7 is axially prestressed against the cylinder 3 via a spring element 9.
  • the spring element 9 has the shape of a collar sleeve with a first collar 11 which is supported on the cylinder 3, and a second collar 12 which is supported on the leakage minimization sleeve 7.
  • the second collar 12 is designed in the manner of a spring arm and rests only on an annular contour 13 on an end face 10 of the Leckageminim istshülse 7 (see Fig. 3). Over the collar 12 thus an axial biasing force can be applied.
  • the leakage minimization sleeve 7 is supported on the cylinder 3 via a footprint 14.
  • the footprint 14 is smaller than the end face 10, since the contact surface 14 is followed by a cone 15 (see FIG. 4). Due to the reduced footprint 14, the sealing effect can be further improved.
  • the cone 15 has a width b which is greater than a width a of the contact surface 14.
  • the spring element 9 has a recess 26 on the circumference.
  • the recess 26 serves to create a pressure equalization within the pressure chamber 8.
  • the first collar 11 of the spring element 9 is also clamped between an upper part 3.1 and a lower part 3.2 of the cylinder 3.
  • the multi-part design of the cylinder 3 facilitates the manufacture of the annular groove 6 and the assembly of the leakage minimization sleeve 7 and the spring element.
  • FIGS. 5 and 6 show alternative embodiments of a spring element 9 for a reciprocating compressor 1 according to the invention.
  • the spring element 9 is designed as a helical compression spring. This requires a larger space than the corrugated spring shown in FIG. 6, so that the height Hi of the annular groove 6 can vary significantly.
  • the height H2 gives the height of the leakage mini- m istshülse 7, which is smaller than the height Hi of the annular groove 6. In this way, the required hydraulic connection of the pressure chamber 8 is made with the compression space 5.
  • the width Bi of the annular groove 6 is also greater than the width B2 of the leakage minimization sleeve 7, so that the difference in width of the width of the pressure chamber 8 benefits.
  • a spring element 9 can be entirely dispensed with. Because due to the difference in area of acted upon in the axial direction with compression space pressure surfaces (end face 10 on the one hand and the footprint 14 forming end faces on the other hand) act on the Leckageminim istshülse 7 hydraulic pressure forces which hold the sleeve 7 in contact with the cylinder 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un compresseur à piston (1) destiné à comprimer un fluide de travail, en particulier un carburant liquide ou gazeux. Le compresseur à piston comprend un piston (4) effectuant un mouvement alternatif dans un alésage (2) d'un cylindre (3) et délimitant dans l'alésage (2) un espace de compression (5) pouvant être rempli par le fluide de travail. Selon l'invention, une gorge annulaire périphérique (6) est formée sur la périphérie intérieure dans le cylindre (3), gorge dans laquelle est reçu un manchon de minimisation de fuites (7) qui définit conjointement avec le cylindre (3) une chambre de compression annulaire (5) qui est reliée hydrauliquement à l'espace de compression (5) de sorte que la même pression règne dans la chambre de pression (8) et dans l'espace de compression (5) et un interstice et donc un certain écoulement dans l'interstice reste entre le piston (4) et le manchon de minimisation de fuites (7) sur toute la plage de pression.
PCT/EP2018/077973 2017-10-27 2018-10-15 Compresseur à piston WO2019081239A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017219341.7 2017-10-27
DE102017219341.7A DE102017219341A1 (de) 2017-10-27 2017-10-27 Kolbenverdichter

Publications (1)

Publication Number Publication Date
WO2019081239A1 true WO2019081239A1 (fr) 2019-05-02

Family

ID=63896122

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2018/077973 WO2019081239A1 (fr) 2017-10-27 2018-10-15 Compresseur à piston

Country Status (2)

Country Link
DE (1) DE102017219341A1 (fr)
WO (1) WO2019081239A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112727736A (zh) * 2020-12-29 2021-04-30 珠海格力电器股份有限公司 泵体组件和流体机械

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018204160A1 (de) 2018-03-19 2019-09-19 Robert Bosch Gmbh Hochdruckförderpumpe und Kraftstofffördereinrichtung für kryogene Kraftstoffe

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5899136A (en) * 1996-12-18 1999-05-04 Cummins Engine Company, Inc. Low leakage plunger and barrel assembly for high pressure fluid system
WO2003010446A1 (fr) 2001-07-25 2003-02-06 Empresa Brasileira De Compressores S.A. - Embraco Systeme de montage conçu pour le piston d'un compresseur alternatif hermetique
DE102008010238A1 (de) * 2008-02-21 2009-08-27 Robert Bosch Gmbh Hochdruckelement für Einspritzanlagen von Brennkraftmaschinen
DE102008040088A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe
JP2010229914A (ja) * 2009-03-27 2010-10-14 Denso Corp 高圧ポンプ
KR101672761B1 (ko) * 2016-07-08 2016-11-04 (주) 아람시스템 정밀 주입 펌프

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5899136A (en) * 1996-12-18 1999-05-04 Cummins Engine Company, Inc. Low leakage plunger and barrel assembly for high pressure fluid system
WO2003010446A1 (fr) 2001-07-25 2003-02-06 Empresa Brasileira De Compressores S.A. - Embraco Systeme de montage conçu pour le piston d'un compresseur alternatif hermetique
DE102008010238A1 (de) * 2008-02-21 2009-08-27 Robert Bosch Gmbh Hochdruckelement für Einspritzanlagen von Brennkraftmaschinen
DE102008040088A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe
JP2010229914A (ja) * 2009-03-27 2010-10-14 Denso Corp 高圧ポンプ
KR101672761B1 (ko) * 2016-07-08 2016-11-04 (주) 아람시스템 정밀 주입 펌프

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112727736A (zh) * 2020-12-29 2021-04-30 珠海格力电器股份有限公司 泵体组件和流体机械
CN112727736B (zh) * 2020-12-29 2022-02-11 珠海格力电器股份有限公司 泵体组件和流体机械

Also Published As

Publication number Publication date
DE102017219341A1 (de) 2019-05-02

Similar Documents

Publication Publication Date Title
EP3655650B1 (fr) Pompe à piston
EP0188730B1 (fr) Pompe à disphragme à diaphragme roulant actionné hydrauliquement
DE102015111175A1 (de) Hydraulikventil und Pleuel mit einem Hydraulikventil
WO2004072477A1 (fr) Pompe haute pression
EP3108137B1 (fr) Pompe à carburant à piston pour moteur à combustion interne
WO2019015863A1 (fr) Pompe a piston, notamment pompe a carburant haute pression destinee a un moteur a combustion interne
WO2019081239A1 (fr) Compresseur à piston
DE102008040088A1 (de) Hochdruckpumpe
DE2204162B2 (de) Spaltdichtung für die Abdichtung hin- und hergehender Maschinenteile
DE102007047419A1 (de) Kolbenpumpe zur Förderung eines Fluids und zugehöriges Bremssystem
DE69915946T2 (de) Dichtung
WO2019015859A1 (fr) Pompe à piston
DE102009047590B4 (de) Kolbenpumpe mit einer Dichtungsanordnung
DE102004011284A1 (de) Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102011075415A1 (de) Zahnpumpe
EP3655649B1 (fr) Pompeà piston, en particulier une pompe à injection de carburant haute pression pour un moteur à combustion
WO2019081237A1 (fr) Compresseur à piston
WO2019115097A1 (fr) Dispositif d'alimentation en carburant pour carburants cryogéniques
DE3542938A1 (de) Kraftstoffeinspritzpumpe
DE4102364A1 (de) Kolbenpumpe
EP2304220A1 (fr) Pompe a haute pression
EP3073095B1 (fr) Vanne hydraulique et bielle avec vanne hydraulique
DE102020203529B3 (de) Anordnung und Verfahren zum Herstellen einer Anordnung für eine Kraftstoffhochdruckpumpe und Kraftstoffhochdruckpumpe für ein Kraftfahrzeug
WO2019081240A1 (fr) Compresseur à piston
DE10355028A1 (de) Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18789051

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18789051

Country of ref document: EP

Kind code of ref document: A1