EP3130803A1 - Dispositif de pompage, en particulier pompe a pistons axiaux pour un dispositif de recuperation de la chaleur perdue d'un vehicule automobile - Google Patents

Dispositif de pompage, en particulier pompe a pistons axiaux pour un dispositif de recuperation de la chaleur perdue d'un vehicule automobile Download PDF

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Publication number
EP3130803A1
EP3130803A1 EP16181718.4A EP16181718A EP3130803A1 EP 3130803 A1 EP3130803 A1 EP 3130803A1 EP 16181718 A EP16181718 A EP 16181718A EP 3130803 A1 EP3130803 A1 EP 3130803A1
Authority
EP
European Patent Office
Prior art keywords
fluid
pumping device
working space
fluid line
line
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.)
Withdrawn
Application number
EP16181718.4A
Other languages
German (de)
English (en)
Inventor
Helge LADISCH
Christian Maisch
Jochen Eggler
Sascha Senjic
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.)
Mahle International GmbH
Original Assignee
Mahle International 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 Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP3130803A1 publication Critical patent/EP3130803A1/fr
Withdrawn legal-status Critical Current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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0016—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a fluid spring
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0033—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a mechanical spring
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0091—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using a special shape of fluid pass, e.g. throttles, ducts

Definitions

  • the invention relates to a pump device, in particular an axial piston pump, for a waste heat utilization device of a motor vehicle.
  • Waste heat utilization devices are used for energy recovery from a waste heat flow of an internal combustion engine of a motor vehicle.
  • Waste heat utilization devices known from the prior art typically comprise a fluid circuit, for example a so-called Clausius-Rankine cycle in which a working fluid circulates. From the heat stored in the working medium mechanical energy is obtained by various state changes in the working fluid, which this is subjected to when flowing through the fluid circuit.
  • a reciprocating or axial piston pump follows the operating principle of a positive-displacement pump in which the so-called displacer in the form of a piston executes a translatory stroke movement within a working volume.
  • the basic idea of the invention is therefore to provide one or more pressure fluctuation compensators in a pump device which serve to equalize the pressure of the fluid delivered by the pump device. Undesirable pressure fluctuations and, associated cavitation, can be kept low in this way or even completely suppressed.
  • One or more of the pressure fluctuation compensators presented here can be arranged in one or more of the fluid lines of the pump device through which the working fluid flows. Said pressure fluctuation compensator is based on the principle of action of a body, the volume of which varies as a function of the fluid pressure of the working medium acting on the pressure fluctuation compensator.
  • a pumping device comprises a working chamber which is partially delimited by a pump housing and which can be filled in a known manner with a working fluid - hereinafter referred to simply as "fluid" for the sake of simplicity.
  • the working volume forming working space is arranged along an axial direction adjustable piston.
  • This piston is adjustable along the axial direction between a first position, in which the working space has a maximum volume, and a second position, in which the working space has a minimum volume.
  • a first fluid line serves to introduce the fluid into the working space.
  • the first fluid line is fluidly connected to the working space by means of an opening which is formed on an end face of the working space opposite the piston in the pump housing.
  • a first valve element is provided for closing the first fluid line against the working space.
  • the first fluid line extends at least in the region of the opening transversely to the axial direction.
  • the pump device also includes a second fluid line for discharging the fluid from the working space, which opens into the working space in the region of the second position of the piston.
  • at least one pressure fluctuation compensator is arranged to minimize pressure fluctuations in the fluid flowing through the pump device.
  • a second valve element for fluid-tight closing of the second fluid line against the working space is present in an opening region of the second fluid line in the working space.
  • the pressure fluctuation compensator is designed to be volume-compressible, such that the volume of the pressure fluctuation compensator varies as a function of the fluid pressure of the fluid acting on the pressure fluctuation compensator. In this way, existing in the fluid pressure fluctuations can be particularly well attenuated or even completely suppressed.
  • the pressure fluctuation compensator comprises a membrane-like, fluid-tight enclosure.
  • the enclosure partially or completely encloses an enclosure interior that is at least partially filled with a gas. This leads to the necessary for pressure equalization volume compressibility of the envelope.
  • the membrane-like, fluid-tight envelope is formed like a tube.
  • the enclosure has an inlet opening and an outlet opening, which is preferably substantially opposite the inlet opening, so that the enclosure is realized as a peripheral boundary of the first and / or second fluid line.
  • the enclosure is disposed in the fluid conduit such that it forms an internal passageway through which the fluid travels and defines a gap between the internal conduit and the conduit walls of the fluid conduit. In this scenario, the closed space between the enclosure and the conduit wall of the fluid conduit is filled with the gas.
  • the first and / or second fluid line with the envelope disposed therein in cross-section perpendicular to the flow direction of the fluid has an annular geometry.
  • the arrangement of the enclosure is realized in such a way that the space filled with gas radially inward of the enclosure and is bounded radially outwardly of the conduit wall of the first and second fluid line.
  • the membrane-like and fluid-tight envelope comprises a resilient wrapping material or consists of such a resilient wrapping material. This allows a simple way to the required for pressure equalization variation of the volume of the envelope.
  • the pressure fluctuation compensator is to be installed at many different locations in the fluid line (s), it is advisable to realize the pressure fluctuation compensator in the form of at least one recess.
  • Said at least one recess is arranged in a line wall delimiting the first or second fluid line and is closed in a fluid-tight manner by means of a membrane-like cover.
  • the recess is filled with the gas in an analogous manner to the variant explained above with a gas enclosing enclosure.
  • a compensator body with closed pores which can be arranged on the inside of the first or second fluid line limiting line wall.
  • the compensator body can be plate-like and have at least one compensator plate.
  • a plate is fastened on the inside to the first or second fluid line, so that a particularly large cross-section with the fluid or working medium of the pump device results for the pressure fluctuation compensator.
  • a biasing means may be provided which controls the pressure fluctuation compensator against the fluid pressure of the fluid flowing through the pumping device.
  • a pretensioning device may be realized approximately in the manner of a spring element, which is arranged in the enclosure or in the recess and is supported to generate a spring force on the enclosure or on the cover which closes the recess.
  • the pumping device may comprise a fluid supply line for introducing the fluid into the first fluid line. Any pressure fluctuations in the fluid which already occur at the inlet of the fluid into the pump device on the suction side can be weakened particularly effectively in this way. Therefore, it is proposed to arrange at least one additional pressure fluctuation compensator in said fluid supply line.
  • fluid supply line discharges tangentially and / or obliquely into the first fluid line.
  • the pumping device may not only have a single, but at least two second fluid lines, all of which open into a common fluid discharge line.
  • a pressure fluctuation compensator is arranged in at least one opening region of the fluid discharge line. In this way, not only the suction side, but also pressure side occurring pressure fluctuations in the fluid can be significantly reduced in the pumping device.
  • the pumping device requires particularly little construction space, in which the first fluid line extends in the region of the aperture in a plane perpendicular to the axial direction and is curved at least in the region of the aperture.
  • the first fluid line may be formed as a closed annular fluid channel which extends completely in the plane perpendicular to the axial direction.
  • Such an annular geometry of the first fluid line has the consequence that the transverse acceleration acting on the fluid as it flows through the fluid channel can be kept relatively low on average. As a result, this measure also has the consequence that a pressure drop in the fluid caused by high transverse accelerations largely disappears.
  • a pressure fluctuation compensator is particularly preferably arranged in the region of the opening.
  • the first valve element protrudes at least partially from the first fluid conduit through the opening into the working space. This means that no additional fluid line has to be provided between the first fluid line and the working space, but that the fluid can be introduced directly from the - preferably annular - first fluid line into the working space of the pump device. In this way, the amount of fluid to be accelerated during the suction of the fluid into the working space is minimized, as a result of which the already explained, in this case acceleration-related Pressure drop of the fluid pressure can be reduced again.
  • the first valve element is an adjustable between an open and a closed position check valve, which is adjusted from the closed to the open position, when the fluid pressure in the first fluid line is greater than in the working space and the pressure difference exceeds a predetermined threshold.
  • a valve element - for discharging the fluid from the working space.
  • second valve element Analogous to the first fluid line, a valve element - hereinafter referred to as "second valve element" - is also provided in an opening area of the second fluid line into the working space for closing the second fluid line.
  • the mouth region of the second fluid line is provided in an axial end section of the working space facing the first fluid line.
  • Structurally particularly simple design and thus associated with reduced manufacturing costs is another preferred embodiment in which the second fluid line opens in a working space bounding peripheral wall of the housing in the working space.
  • first fluid conduit extends the working space along the axial direction.
  • the second valve element may also be a non-return valve which can be adjusted between an open and a closed position.
  • the second check valve is then arranged such that it is adjusted from the closed to the open position when the fluid pressure in the working space is greater than in the second fluid line and the pressure difference exceeds a predetermined threshold. Accordingly, the second check valve can be returned to the closed position when the pressure difference falls below said threshold again.
  • an orifice of the second fluid conduit into the working space with respect to its axial position may be arranged such that the piston just does not close it in its second position.
  • the first valve element protrudes into the working space in such a way that the remaining volume between the Piston in its second position and the first valve element assumes a minimum value. This measure counteracts unwanted flow and compression losses of the fluid in the working volume.
  • a resilient element can be arranged in the working space. This is preferably supported at one end on the first valve element and the other end on the piston and thus biases the piston towards the first position.
  • the invention therefore also relates to a pump arrangement with three previously proposed pump devices according to the invention, whose working chambers are arranged parallel to each other with the openings between the working space and the first fluid line in each case with respect to the axial direction.
  • the arrangement of the three working chambers with the openings between the first fluid line and the working space in this case has a 120 ° rotational symmetry in a cross section perpendicular to the axial direction with respect to a predefined point of symmetry.
  • the three first fluid lines are formed as a common annular fluid channel with the already mentioned point of symmetry as the ring center of the annular fluid channel.
  • the space required for the three pumping devices can be kept low.
  • the symmetrical design of the three pumping devices moreover leads to the fact that even with the fluidic interconnection of three pumping devices the occurrence of undesired cavitation can be largely or even completely avoided.
  • the invention relates to a waste heat utilization device which comprises a fluid circuit through which a working fluid flows or which can flow.
  • a waste heat utilization device which comprises a fluid circuit through which a working fluid flows or which can flow.
  • an above-presented, inventive pumping device or a previously presented, inventive pumping arrangement with three pumping devices is arranged.
  • FIG. 1 Illustrates in a perspective view an example of a pump arrangement 20 according to the invention
  • FIG. 2 shows a detailed representation of the FIG. 1 in which the structure of a pumping device 1 of the pumping arrangement 20 is shown in greater detail.
  • the FIG. 3 again shows a detailed view of Figure 2 in the region of a working space 3 of the pumping device first
  • the pump arrangement 20 comprises three pump devices 1, each designed as a lifting or axial piston pump, which are realized to form the pump arrangement 20 in the form of a tripod arrangement.
  • the respective pistons 2 of the three pumping devices 1 and the working chambers 3 accommodating the respective pistons 2, each of which is delimited by a pump housing 4, are arranged parallel to one another with respect to their axial axis.
  • an adjustable along an axial direction A piston 2 is arranged in each of the three working spaces 3.
  • Each of the three pistons 2 is axially adjustable between a first position, in which the working space 3 has a maximum volume, and a second position, in which the working space 3 has a minimum volume.
  • a common electric motor 22 which is arranged in a pump housing 4 against the axial direction A extending motor housing 21.
  • the control of the electric motor 22 can be carried out with the aid of an electrical / electronic control unit 25, which is fastened on an axially remote from the pump housing 4 side of the motor housing 22 at this.
  • a first valve element 10 for closing the first fluid line 5 is provided in the first fluid line 5.
  • the first valve element 10 projects through the opening 9 into the working space 3, preferably in such a way that the dead volume of the working space becomes minimal.
  • the first valve element 10 is a check valve 11 that can be adjusted between an open and a closed position. In the closed position, the first valve element 10 closes the first fluid line 5 in a fluid-tight manner against the working space 3. In the open position, the first valve element 10 releases the fluid connection between the first fluid line 5 and the working space 3, so that the fluid can be introduced from the first fluid line 5 into the working space 3.
  • the check valve 11 is moved from its closed position to its open position when the fluid pressure in the first fluid line 5 is greater than in the working space 3 and the pressure difference exceeds a predetermined threshold. This is done by an axial movement of the piston 2 from the opening 9 away.
  • Pumping device 1 also includes a fluid supply line 24 for introducing the fluid into first fluid line 5.
  • Fluid supply line 24 opens tangentially into first fluid line 5 designed as annular fluid channel 23.
  • fluid supply line 24 can also be inclined into first fluid line 5 lead. This may mean in particular that in a longitudinal section of the pump device 1 along the axial direction A, the fluid supply line 24 forms an acute angle with the plane perpendicular to the axial direction A, in which the annular Fluid channel 23 is arranged.
  • the first fluid line 5 extends the working space 3 along the axial direction A.
  • a second fluid line 6 is provided which is in the region of the second position of the piston 2 - this position is in FIG. 2 and in the detail of the FIG. 3 shown - opens into the working space 3.
  • the mouth region 12 of the second fluid line 6 is therefore -as well as the first fluid line 5 introduced at the end-arranged in an axial end section 14 of the working space 3 facing the first fluid line 5.
  • the second fluid line 6 opens into the working space 3 in a circumferential wall 15 of the pump housing 4 delimiting the working space 3.
  • the second fluid line 6 opens obliquely into the working space 3 relative to the axial direction A.
  • An orifice 16 of the second fluid line 6 is in such an axial position arranged that the piston 2 just does not close the mouth opening 16 in its second position.
  • a second valve element 13 is also provided in the mouth region 12 of the second fluid line 6 into the working space 3 for selectively sealing the second fluid line 6 in a fluid-tight manner with respect to the working space.
  • the second valve element 13 is, as the first valve element 10, realized as a check valve 17. In contrast to the first valve element 10, however, it is adjusted from the closed to the open position when the fluid pressure in the working chamber 3 is greater than in the second fluid line and the pressure difference exceeds a predetermined threshold. This happens when the piston is moved along the axial direction A to the opening 9.
  • pressure fluctuation compensators 30 are arranged to minimize pressure fluctuations in the fluid flowing through the pumping device 1.
  • the pressure fluctuation compensators 30 are each arranged in the region of an opening 9 in the realized as an annular fluid passage 23 first fluid line 5.
  • at least one additional pressure fluctuation compensator 30 may be arranged.
  • FIG. 2 The second fluid lines 6 open into a common fluid discharge line 8. Also in the mouth region 25 of the fluid discharge line 8, in which the second fluid lines 6 open into the fluid discharge line 6, a pressure fluctuation compensator 30 can be arranged.
  • the pressure fluctuation compensators 30 are shown roughly schematically in the form of a circle, respectively, to illustrate their position in the pumping device.
  • FIG. 4 shows a schematic representation of a first implementation of the pressure fluctuation compensator 30 essential to the invention, as it can be arranged in the first fluid line 5, in the second fluid line 6, in the fluid supply channel 24 or in the fluid discharge channel 8.
  • the pressure fluctuation compensator 30 is disposed in the first fluid passage 5.
  • the FIG. 4 shows the first fluid line 5 in a cross section perpendicular to the main flow direction X of the fluid flowing through the first fluid line 5.
  • the first fluid line 5 is delimited by at least one conduit wall 26.
  • the pressure fluctuation compensator 30 includes a diaphragm-type formed fluid-tight enclosure 31 that encloses a sheath interior 32.
  • the envelope interior 32 is filled with a gas 33.
  • the material for the envelope 31 is a fluid-tight elastomer into consideration.
  • the pressure fluctuation compensator 30 is formed such that the Volume of the pressure fluctuation compensator 30 varies depending on the pressure acting on the pressure fluctuation compensator 30 fluid pressure of the working medium.
  • the pressure fluctuation compensator 30 can be made volume-compressible.
  • FIG. 4 encloses the envelope 31, the envelope interior 32 completely. This means that the gas 33 is fluidically separated from the fluid flowing through the first fluid line 5 and to be delivered by the pumping device 1-indicated schematically in FIG. 4 and designated by the reference numeral 34.
  • the cross section of the FIG. 5 shows a variant of the example of FIG. 4 ,
  • the envelope 32 does not completely envelop the envelope interior 33, but is formed as a tube 37 and has an inlet opening 35 at the end and an outlet opening 36 opposite the inlet opening 35.
  • This scenario is described in FIG FIG. 6 reproduced, the first fluid line 5 in a longitudinal section along the main flow direction X shows.
  • the sheath 31 forms an inner channel 38 through which the fluid 34 can flow.
  • a space 39 between the conduit wall 26 of the first fluid conduit 5 and the enclosure 31 is filled with the gas 33.
  • the cross section shown has the first fluid line 5 with the envelope 31 disposed therein an annular geometry.
  • the gap 39 filled with gas 33 is bounded radially inward by the enclosure 31 and radially outward by the conduit wall 26 of the first fluid conduit 5.
  • the membranous envelope 31 of the FIGS. 4 to 6 may comprise a resilient wrapping material or even consist of a resilient wrapping material.
  • FIG. 7 shows a further variant of the pressure fluctuation compensator 30 essential to the invention
  • FIG. 7 shows in an analogous manner to FIG. 6 the first fluid line 5 in longitudinal section along the Haupt manströmungscardi X of the fluid.
  • the pressure fluctuation compensator 30 comprises a recess 41, which is formed in the conduit wall 26 delimiting the first fluid line 5.
  • the recess 41 is closed fluid-tight by means of a membrane-like cover 40, which is part of the pressure fluctuation compensator 30.
  • said recess 41 is filled with the gas 33.
  • the pressure fluctuation compensator 30 formed as a closed-porous Kompensator body 42 which is mounted on the first fluid line 5 bounding the conduit wall 26. If as little installation space as possible is to be lost for the pressure fluctuation compensator 30, it is advisable to design the compensator body 42 in a plate-like manner. In FIG. 8 is on the inside of the housing wall 26 such a compensator plate 43 attached, which acts as a pressure fluctuation compensator 30.
  • An improved pressure equalization by means of the pressure fluctuation compensator 30 can be achieved when the pressure fluctuation compensator 30 is provided with biasing means which biases the pressure fluctuation compensator 30 against the fluid pressure of the fluid 34 flowing through the pumping device 1.
  • biasing means may be formed in the manner of a spring element 44, which, as in the FIGS. 4, 5 and 7 roughly indicated in the envelope interior 32 or in the recess 41 and is supported on the envelope 31 and the cover 40 and the conduit wall 26.
  • a resilient element 19 may be provided in the working space 3. This is supported accordingly FIG. 3 , which at one end on the first valve element 10 and the other end on the piston 2 and thus biases the piston 2 to the first position.
  • FIG. 9 shows the structure of the FIG. 2 in a cross section perpendicular to the axial direction A in a rough schematic representation.
  • the three working spaces 3 of the three pumping devices 1 - in FIG. 4 indicated by dashed lines - are arranged along the axial direction A parallel to each other.
  • FIG. 9 clearly shows, the arrangement of the three working spaces 3 in cross-section perpendicular to the axial direction A with respect to a predefined point of symmetry S a 120 ° rotational symmetry.
  • the three first fluid lines 5 are formed as a common annular fluid channel 2 with the point of symmetry S as the ring center M.
  • the formation of the first fluid line 5 can be used as an annular fluid channel 23 to supply the working spaces 3 of all three pumping devices 1 in the manner described above with the working fluid, ie the fluid. This ensures that the formation of unwanted cavitation can be largely or even completely prevented both in the fluid channel 23 and in the three working spaces 3.
  • the three second fluid lines 6 open corresponding to the FIG. 2 in a common fluid discharge line. 8

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP16181718.4A 2015-08-13 2016-07-28 Dispositif de pompage, en particulier pompe a pistons axiaux pour un dispositif de recuperation de la chaleur perdue d'un vehicule automobile Withdrawn EP3130803A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015215477.7A DE102015215477A1 (de) 2015-08-13 2015-08-13 Pumpvorrichtung, insbesondere Axialkolbenpumpe, für eine Abwärmenutzungseinrichtung eines Kraftfahrzeugs

Publications (1)

Publication Number Publication Date
EP3130803A1 true EP3130803A1 (fr) 2017-02-15

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Application Number Title Priority Date Filing Date
EP16181718.4A Withdrawn EP3130803A1 (fr) 2015-08-13 2016-07-28 Dispositif de pompage, en particulier pompe a pistons axiaux pour un dispositif de recuperation de la chaleur perdue d'un vehicule automobile

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EP (1) EP3130803A1 (fr)
DE (1) DE102015215477A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019138281A1 (fr) * 2017-12-27 2019-07-18 ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング Dispositif de commande de la pression hydraulique de frein comportant une pompe à pistons axiaux et des amortisseurs en ligne

Citations (5)

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Publication number Priority date Publication date Assignee Title
DE19654098A1 (de) * 1996-12-23 1998-06-25 Braun Ag Pulsationsdämpfer für Munddusche
EP0961023A2 (fr) * 1998-05-28 1999-12-01 Mitsubishi Denki Kabushiki Kaisha Pompe à haute pression pour systèmes d'injection de combustible
EP1411236A2 (fr) * 2002-10-19 2004-04-21 Robert Bosch Gmbh Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne
US20110110807A1 (en) * 2009-02-18 2011-05-12 Denso Corporation High-pressure pump
DE102013213614A1 (de) * 2013-07-11 2015-01-15 Volkswagen Aktiengesellschaft Axialkolbenmaschine

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DE223130C (de) * 1940-07-16 1910-06-15 Erik Anton Rundlöf Regelungsvorrichtung für brennstoffpumpen
DE1989685U (de) * 1967-04-22 1968-07-18 Rau Swf Autozubehoer Fluessigkeitsfoerdergeraet.
DE8205932U1 (de) * 1982-03-04 1982-07-08 Pumpenfabrik Urach, 7432 Urach Kolbenpumpe mit pulsationsdaempfer-anordnung
DE3914954A1 (de) * 1988-07-07 1990-01-11 Teves Gmbh Alfred Kolbenpumpe
DE3912937A1 (de) * 1989-04-20 1990-10-25 Teves Gmbh Alfred Daempfungseinrichtung fuer hydraulische verdraengerpumpen
DE9114384U1 (de) * 1991-11-19 1992-03-05 Gotec S.A., Sion Schwingkolbenpumpe
JP3999855B2 (ja) * 1997-09-25 2007-10-31 三菱電機株式会社 燃料供給装置
JP2000045906A (ja) * 1998-07-29 2000-02-15 Mitsubishi Electric Corp 高圧燃料ポンプ装置
JP3823060B2 (ja) * 2002-03-04 2006-09-20 株式会社日立製作所 高圧燃料供給ポンプ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19654098A1 (de) * 1996-12-23 1998-06-25 Braun Ag Pulsationsdämpfer für Munddusche
EP0961023A2 (fr) * 1998-05-28 1999-12-01 Mitsubishi Denki Kabushiki Kaisha Pompe à haute pression pour systèmes d'injection de combustible
EP1411236A2 (fr) * 2002-10-19 2004-04-21 Robert Bosch Gmbh Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne
US20110110807A1 (en) * 2009-02-18 2011-05-12 Denso Corporation High-pressure pump
DE102013213614A1 (de) * 2013-07-11 2015-01-15 Volkswagen Aktiengesellschaft Axialkolbenmaschine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019138281A1 (fr) * 2017-12-27 2019-07-18 ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング Dispositif de commande de la pression hydraulique de frein comportant une pompe à pistons axiaux et des amortisseurs en ligne
US11767002B2 (en) 2017-12-27 2023-09-26 Robert Bosch Gmbh Brake hydraulic pressure controller

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