EP4080047B1 - Dispositif de pompe - Google Patents

Dispositif de pompe Download PDF

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Publication number
EP4080047B1
EP4080047B1 EP22167974.9A EP22167974A EP4080047B1 EP 4080047 B1 EP4080047 B1 EP 4080047B1 EP 22167974 A EP22167974 A EP 22167974A EP 4080047 B1 EP4080047 B1 EP 4080047B1
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EP
European Patent Office
Prior art keywords
pump
piston
valve
housing
fluid
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
EP22167974.9A
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German (de)
English (en)
Other versions
EP4080047A1 (fr
EP4080047C0 (fr
Inventor
Frank Kattler
Christian Groh
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.)
Hydac Fluidtechnik GmbH
Original Assignee
Hydac Fluidtechnik 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 Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP4080047A1 publication Critical patent/EP4080047A1/fr
Application granted granted Critical
Publication of EP4080047B1 publication Critical patent/EP4080047B1/fr
Publication of EP4080047C0 publication Critical patent/EP4080047C0/fr
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Anticipated expiration legal-status Critical

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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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • 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
    • F04B13/00—Pumps specially modified to deliver fixed or variable measured quantities
    • 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
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/121—Valves; Arrangement of valves arranged in or on pistons the valve being an annular ring surrounding the piston, e.g. an O-ring
    • 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
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/122—Valves; Arrangement of valves arranged in or on pistons the piston being free-floating, e.g. the valve being formed between the actuating rod and the 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0073—Piston machines or pumps characterised by having positively-driven valving the member being of the lost-motion type, e.g. friction-actuated members, or having means for pushing it against or pulling it from its seat
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports

Definitions

  • the invention relates to a pump device having the features in the preamble of claim 1.
  • a device for providing fluids under a predeterminable pressure for the pressure supply of a consumer such as a working unit of a selective catalytic reduction system (SCR system) for exhaust gas aftertreatment of internal combustion engines, with at least one pump device which, in a fluid circuit formed between a fluid supply and a consumer, takes the fluid in question from the fluid supply and supplies it to the consumer.
  • SCR system selective catalytic reduction system
  • the known pump device requires a conventional pressure supply in the form of a drivable hydraulic pump to operate.
  • a system for exhaust gas aftertreatment in an internal combustion engine comprising a pump device with a pump piston arranged to be longitudinally movable in a pump housing, which acts on both an inlet valve and an outlet valve, controlled by an actuating magnet device, the inlet valve opening during the intake stroke of the pump piston and the outlet valve during its discharge stroke.
  • the known solution is used for a metered supply of a freezable substance, in particular in the form of an aqueous urea solution.
  • a compensation device acts on a fluid or pump chamber in such a way that a volume expansion of the substance within this fluid or pump chamber, which accompanies an increase in the fluid pressure during freezing, is compensated.
  • the DE 1 301 956 B describes a pump device with the features in the preamble of claim 1 with a pump piston arranged longitudinally displaceably in a pump housing, which, controlled by an actuating magnet device, opens an outlet valve for a fluid discharge during a delivery stroke, wherein in a pump chamber of the pump housing during a suction stroke the pump piston generates a negative pressure and, when passing over a control edge delimiting the pump chamber, a Establishes a fluid connection between a fluid inlet in the pump housing and the pump chamber in such a way that the pump chamber is filled under the effect of the negative pressure prevailing therein with a filling volume which results from a fluid flow which is guided along the outer circumference of parts of the pump piston in the direction of the outlet valve, and then this filling volume is discharged from the pump chamber via the outlet valve during the delivery stroke.
  • the invention is based on the object of providing a further alternative to the known systems and pump devices while retaining the advantages of the known systems and pump devices, which is characterized by a high degree of functional reliability and which can be implemented in a space-saving and cost-effective manner.
  • a pump device having the features of patent claim 1 in its entirety solves this problem.
  • the pump housing is connected to a valve housing which accommodates the outlet valve by means of an annular seal attached to the front side.
  • the pump piston Due to the fact that in a pump chamber of the pump housing the pump piston generates a negative pressure during a suction stroke and, when passing over a control edge delimiting the pump chamber, creates a fluid connection between a fluid inlet in the pump housing and the pump chamber in such a way that the pump chamber is filled under the effect of the negative pressure prevailing in it with a filling volume that results from a fluid flow that is guided along the outer circumference of parts of the pump piston in the direction of the outlet valve, and then in the delivery stroke
  • This filling volume is discharged from the pump chamber via the outlet valve, a fluid conveying device is created which does not require an additional inlet valve in addition to the outlet valve.
  • the pump chamber in the pump housing is filled with fluid exclusively via the control movement of the pump piston, which is then discharged via the outlet valve in the subsequent delivery stroke by means of the pump piston.
  • the negative pressure in the pump chamber initially increases until the pump piston moves backwards over the control edge on the pump housing in the direction of the fluid supply, suddenly opening a fluid connection between the fluid inlet and the pump chamber.
  • the fluid then flows from the inlet into the pump chamber at high flow speed through the annular gap formed in this way.
  • the fluid flowing past the outer circumference of parts of the pump piston into the pump chamber when the control edge is released is forcibly discharged as filling volume in the subsequent forward delivery stroke by means of the pump piston via the outlet valve, which then opens.
  • an additional inlet valve in the form of a spring-loaded check valve does not have to be regularly controlled by the pump device or its fluid flow during the intake stroke, the stroke or load changes from intake stroke to delivery stroke can be carried out in rapid succession, so that very high cycle rates are achieved for the pump device according to the invention in the smallest installation space.
  • By eliminating an inlet valve a component is saved, which is cost-effective, and no movable valve component can fail, which increases overall functional reliability.
  • the outlet valve consists of a spring-loaded check valve, the valve piston of which, in the closed state, closes the pump chamber shuts off from a fluid outlet and is arranged coaxially to the pump piston.
  • the force control direction for the valve piston of the check valve is in the same axis as the travel axis of the pump piston, so that direct control of the outlet valve is possible with centered force introduction onto the valve piston. The latter excludes obstacles in the operation of the outlet valve.
  • the pump piston moves the valve piston of the check valve into its open position as part of its delivery stroke due to the fluid volume displaced in this way.
  • the fluid volume forced out of the pump chamber by the pump piston leads to the check valve being completely opened, so that a pure fluid actuation for the check valve is provided by the pump piston, which allows for unhindered operation.
  • the pump piston is reduced in diameter in the direction of its free end face facing the valve piston compared to the diameter in the area of the guide of the pump piston in the pump housing.
  • the pump piston starting from its guide diameter in the pump housing, has a recess in the form of a diameter reduction, which merges into a truncated cone as a flow guide device, which is followed by a further diameter reduction of the pump piston in the form of a control cylinder.
  • the recess and the flow guide device both as an integral part of the pump piston, result in optimal fluid guidance with the corresponding introduction of the filling volume into the pump chamber, whereby the recess on the pump piston contributes to the fact that the negative pressure generation in the pump chamber is almost suddenly eliminated by means of the pump piston. and the inflow of the fluid from the fluid supply into the pump chamber for the subsequent discharge process can take place within the framework of a delivery stroke.
  • the pump chamber has various chambers which are provided with different diameters and of which a middle chamber has at least partially such a diameter that an annular gap is formed between the pump housing and the outer wall of the pump piston with its outer diameter in the area of its guide in the pump housing.
  • the annular gap mentioned ensures unhindered operation during the intake stroke and the immediate build-up of a corresponding negative pressure in the pump chamber, in particular in the chamber of the pump chamber with the largest cross-section.
  • valve housing has a part of the fluid inlet and that the pump housing is accommodated in the valve housing.
  • the actuating magnet device is connected to the valve housing, which is fixed together with the pump housing in the manner of a screw-in cartridge in a valve block, which has parts of the fluid inlet and outlet.
  • the main components pump housing with pump piston, valve housing and actuating magnet device.
  • the main components which can be screwed together in this way, can be easily adapted in size depending on the fluid volume to be controlled and can be put together in a cost-effective manner to form an overall pump device.
  • the pump piston executes a delivery stroke when the actuating magnet device is actuated and that, by means of an energy store, preferably in the form of a compression spring, the pump piston executes a suction stroke in the opposite direction when the actuating magnet device is not actuated. Therefore, the actuating magnet device only needs to be energized for the delivery stroke and, when not actuated, the pump piston is automatically moved by means of an energy store into a rear starting position corresponding to the suction stroke, which enables extremely energy-saving operation for the pump device.
  • an energy store preferably in the form of a compression spring
  • the pump device after the Fig.1 has a pump piston 12 arranged longitudinally in a pump housing 10, which is controlled by an actuating magnet device 14 during a delivery stroke in the direction of the Fig.1 viewed from right to left, an outlet valve 16 opens for fluid discharge by means of fluid pressure. If the pump piston 12 moves in the direction of the Fig.1 viewed in the opposite direction from left to right from a forward to a rearward position, it generates a negative pressure in a pump chamber 18 of the pump housing 10 during the suction stroke. The pump piston 12 then travels over an annular control edge 20 in its return movement.
  • the pump chamber 18 is filled with the filling volume under the effect of the negative pressure prevailing in it, which results from a fluid flow that is guided on the outer circumference 24 from front parts of the pump piston 12 in the direction of the outlet valve 16, this filling volume can be displaced at the front in the subsequent delivery stroke of the pump piston 12 with the outlet valve 16 open and discharged from the pump device for further use via a fluid outlet 26.
  • the fluid inlet 22 consists of several holes 30 arranged diametrically to a longitudinal axis 28 of the pump device, which extend radially through the pump housing 10 at the same height and transverse to the longitudinal axis 28.
  • the inner, free end of each hole 30 opens into a circumferential radial recess 32 through which the pump piston 12 can pass and whose outer diameter is larger at every point than the diameter of the pump chamber 18 at every point.
  • the annular control edge 20, which is designed to be continuous, is thus formed by a transition corner or edge, namely at the point of transition of the pump chamber 18 into the radial recess 32.
  • the outlet valve 16 is formed from a spring-loaded check valve, the valve piston 34 of which is shown in the Fig.1 and 2 in the closed state, it blocks the pump chamber 18 from the fluid outlet 26 and is arranged coaxially to the pump piston 12.
  • the valve piston 34 is pot-shaped and accommodates in its pot space parts of a return spring 36 designed as a compression spring, which is supported with one of its free ends on the valve piston 34 and with its other end in a housing receptacle 38 which is closed at the bottom and is preferably an integral part of a valve housing 40.
  • valve piston 34 If the valve piston 34 is opened against the effect of the return spring 36, a locking pin 42 arranged on the free end face of the valve piston 34 releases an annular valve seat 44 on the valve housing 40 and fluid can be discharged from the pump chamber 18 past the valve seat 44 in the direction of the fluid outlet 26 from the pump device.
  • a delivery stroke with the pump piston 12 is necessary, during which the pump piston 12 pushes the fluid in the pump chamber 18 forwards after moving forward over the control edge 20 and in the process moves the spring-loaded valve piston 34 into its open position away from the valve seat 44.
  • valve piston 34 can return to its closed position shown and the pump piston 12 moves backwards, generating a corresponding negative pressure in the pump chamber 18, until the pump piston 12 again moves backwards over the control edge 20 for a new fluid filling process and, for example, Fig.1 and 2 shown rear position.
  • the valve seat 44 is designed in the form of an annular contact surface arranged in the valve housing 40, which also allows a kind of line contact between the locking pin 42 and adjacent parts of the valve housing 40.
  • the pump piston 12 is designed to be reduced in diameter in the direction of its free end face facing the valve piston 34 compared to the diameter in the region of the guide 46 of the rod-like pump piston 12 in the pump housing 10.
  • a recess 48 in the form of a diameter reduction merges seamlessly into a truncated cone 50 as a flow guide device, which is followed by a further diameter reduction of the pump piston 12 in the form of an elongated control cylinder 52.
  • the recess 48 forms a rectangular control edge which interacts with the control edge 20 on the pump housing 10 to control the fluid flow.
  • the angle of the control cone in the form of the truncated cone 50 is approximately 45° when viewed in the direction of the longitudinal axis 28, and the truncated cone merges with a corresponding rounded arc on both its base surface and its cover surface into the stepped recess 48 or into the control cylinder 52, the free cross-sectional area of which is smaller than the free cross-sectional area of the pump chamber 18 in the area of the transition to housing parts of the valve housing 10 in the area of the valve seat 44.
  • the pump chamber 18 has various chambers 54, 56 and 58, which are provided with different diameters and of which a middle chamber 56 has at least partially such a diameter that between the pump housing 10 and the outer wall 60 of the pump piston 12 with its outer diameter in the region of its guide in the pump housing 10 an annular gap 62 is formed, which in the Fig.2
  • the dashed line is intended to fictitiously represent the distance between the pump piston 12 and the pump housing 10, provided that the pump piston 12 assumes one of its respective front travel positions.
  • the pump housing 10 is connected to the valve housing 40 by means of a ring seal 64 attached to the front side, which centrally accommodates the outlet valve 16 as seen in the direction of the fluid outlet 26.
  • the valve housing 40 has a part of the fluid inlet 22.
  • further diametrically Through holes 66 arranged in the valve housing 40 are arranged in relation to the longitudinal axis 28 and are arranged at the same height as the holes 30 in the pump housing 10; however, they have a larger diameter.
  • the valve housing 40 is designed in the manner of a screw-in cartridge and is accommodated in a central cuboid-shaped valve block 70 via a screw-in section 68 with a fluid inlet 22 transverse to the longitudinal axis 28 and with a fluid outlet 26 along the longitudinal axis 28.
  • the radial recess 32 in the pump housing 10 is therefore permanently in fluid communication with the fluid inlet 22 in the valve block 70 via the holes 30 and 66.
  • the actuating magnet device 14 is used to control the pump piston 12.
  • the actuating magnet device 14 is of a conventional design and has a magnet armature 74 which can be actuated via an energizable coil 72 and which is guided longitudinally in a pole tube 76, specifically in a corresponding armature space 78 which has a so-called anti-stick disk 80 on its one free end face, viewed in the direction of the pump piston 12.
  • the pole tube 76 is fixed to the valve housing 40 with associated wall parts via a further screw-in section 82. Furthermore, in the fixed state, the free end face of the pole tube 76 presses the pump housing 10 via the flexible ring seal 64 onto the associated contact wall of the valve housing 40.
  • Longitudinal channels 84 arranged in the magnet armature 74 ensure pressure-balanced operation for the magnet armature 74 from its Fig.1 shown right stop position into its opposite front operating position in the direction of the anti-stick disk 80 and vice versa.
  • the magnet tanker 74 takes along a rod part 86, which accordingly moves the pump piston 12 from its position in the Fig.1 shown right, rear position to the left into a front actuating position.
  • the pump piston 12 moves under the effect of an energy storage device in the form of the compression spring 88 to its maximum intake stroke position, whereby the rod 86 is reset and the magnet armature 74 is thereby moved to its Fig.1 shown starting position.
  • the compression spring 88 is supported with one free end on a free front side of the pump housing 10 and with its other free end on a system extension on the pump piston 12.
  • the pole tube 76 has a through channel 90 which connects the armature chamber 78 with a piston chamber 92 in a media-conducting manner, which, as part of the pump housing 10, accommodates parts of the pump piston 12 with the compression spring 88.
  • the pump piston 12 can be actuated in a short time sequence by controlling the actuating magnet of the magnetic device 14, so that a quasi-continuous pump operation is ensured at the point of fluid discharge 26 in the valve block 70, whereby only a small amount of volume is discharged in view of the small volume of the pump chamber 18.
  • the magnetic device 14 is closed on the outside by a closure plug 94, which is flanged to the pole tube 76 on its right-hand free end face.
  • a screw-on nut 96 covers the connection between the closure plug 94 and the pole tube 76 on the outside.
  • the pump piston 12 opens the valve piston 34 of the check valve preferably exclusively by applying a corresponding fluid pressure, whereby the pin-like control cylinder 52 serves to minimize the dead volume in this area, which results in better control efficiency.
  • the control pin 52 it is still within the scope of the solution according to the invention to also use the control pin 52 for a mechanical opening process of the valve piston 34 if necessary.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (9)

  1. Installation de pompage comprenant un piston (12) de pompe, qui est monté mobile longitudinalement dans un corps (10) de pompe et qui, en étant commandé par un dispositif (14) magnétique d'actionnement, commande, lors d'une course de refoulement, une soupape (16) de sortie pour une distribution de fluide, dans lequel, dans un espace (18) de pompage du corps (10) de la pompe, le piston (12) de la pompe produit, lors d'une course d'aspiration, une dépression et ménage, par un franchissement d'un bord (20) de commande délimitant l'espace (18) de pompage, une communication fluidique entre une admission (22) de fluide dans le corps (10) de la pompe et l'espace (18) de pompage, de manière à ce que l'espace (18) de pompage soit, sous l'effet de la dépression qui y règne, rempli d'un volume de remplissage, qui provient d'un courant de fluide, qui passe sur le pourtour (24) extérieur de parties du piston (12) de la pompe en direction de la soupape (16) de sortie et ensuite dans la course de refoulement, ce volume de remplissage est, en passant par la soupape (16) de sortie, sorti de l'espace (18) de pompage, caractérisée en ce que le corps (10) de la pompe se raccorde, par une garniture (64) d'étanchéité annulaire montée du côté frontal, à un corps (40) de la soupape, qui loge la soupape (16) de sortie.
  2. Installation de pompage suivant la revendication 1, caractérisée en ce que la soupape (16) de sortie est constituée d'un clapet antiretour, qui est soumis à l'action d'un ressort et dont le piston (34) fait obstacle, à l'état de fermeture de l'espace (18) de pompage, à une évacuation (26) de fluide et est monté coaxialement au piston (12) de la pompe.
  3. Installation de pompage suivant la revendication 1 ou 2, caractérisée en ce que le piston (12) de la pompe, lors de sa course de refoulement, met, par le volume de fluide ainsi refoulé, le piston (34) du clapet antiretour dans sa position d'ouverture.
  4. Installation de pompage suivant l'une des revendications précédentes, caractérisée en ce que le piston (12) de la pompe est, dans la direction de son côté frontal libre, tourné vers le piston (34) de la soupape, réduit en diamètre par rapport au diamètre dans la partie du guidage (46) du piston (12) de la pompe dans le corps (10) de la pompe.
  5. Installation de pompage suivant l'une des revendications précédentes, caractérisée en ce que le piston (12) de la pompe a, à partir de son diamètre (46) de guidage dans le corps (10) de la pompe, un ressaut (48) sous la forme d'une réduction de diamètre, qui se transforme en un tronc (50) de cône, comme dispositif de conduite d'écoulement, auquel se raccorde une autre réduction de diamètre du piston (12) de la pompe sous la forme d'un cylindre (52) de commande.
  6. Installation de pompage suivant l'une des revendications précédentes, caractérisée en ce que l'espace (18) de pompage a diverses chambres (54, 56, 58), qui sont pourvues de diamètres différents et dont une chambre (56) médiane a au moins en partie un diamètre tel qu'il est formé un intervalle (62) annulaire entre le corps (10) de la pompe et la paroi (60) extérieure du piston (12) de la pompe par son diamètre extérieur dans la partie de son guidage dans le corps (10) de la pompe.
  7. Installation de pompage suivant l'une des revendications précédentes, caractérisée en ce que le corps (40) de la soupape a une partie d'admission (22) de fluide et en ce que le corps (10) de la pompe est reçu dans le corps (40) de la soupape.
  8. Installation de pompage suivant l'une des revendications précédentes, caractérisée en ce que le dispositif (14) magnétique d'actionnement est relié au corps (40) de la soupape, qui ensemble avec le corps (10) de la pompe est fixé à la manière d'une cartouche à visser dans un bloc (70) de soupape, qui a des parties de l'admission et de l'évacuation (22, 26) de fluide.
  9. Installation de pompage suivant l'une des revendications précédentes, caractérisée en ce que le piston (12) de la pompe exécute, lorsque le dispositif (14) magnétique d'actionnement est actionné, une course de refoulement et en ce que, au moyen d'un accumulateur d'énergie, de préférence sous la forme d'un ressort (88) de compression, dans l'état non actionné du dispositif (14) magnétique d'actionnement, le piston (12) de la pompe exécute une course d'aspiration dans le sens contraire.
EP22167974.9A 2021-04-22 2022-04-12 Dispositif de pompe Active EP4080047B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102021002116.9A DE102021002116A1 (de) 2021-04-22 2021-04-22 Pumpenvorrichtung

Publications (3)

Publication Number Publication Date
EP4080047A1 EP4080047A1 (fr) 2022-10-26
EP4080047B1 true EP4080047B1 (fr) 2024-06-05
EP4080047C0 EP4080047C0 (fr) 2024-06-05

Family

ID=81307449

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22167974.9A Active EP4080047B1 (fr) 2021-04-22 2022-04-12 Dispositif de pompe

Country Status (2)

Country Link
EP (1) EP4080047B1 (fr)
DE (1) DE102021002116A1 (fr)

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1719644U (de) * 1953-02-28 1956-03-29 Limon Fluhme & Co De Kolbenpumpe, insbesondere fuer schmiermittel.
DE1295376B (de) * 1962-02-14 1969-05-14 Tecalemit Gmbh Deutsche Schmiersystem fuer Fahrzeuge oder Maschinen
DE1301956B (de) * 1966-04-02 1969-08-28 Eberspaecher J Brennstoff-Kolbenpumpe
US3468257A (en) * 1966-04-02 1969-09-23 Eberspaecher J Liquid pump valve actuating arrangement
DE102012010980A1 (de) 2012-06-02 2013-12-05 Hydac Electronic Gmbh System zur Abgasnachbehandlung bei Verbrennungsmotoren
DE102018001523A1 (de) 2018-02-27 2019-08-29 Hydac Electronic Gmbh Einrichtung zur Bereitstellung von unter einem vorgebbaren Druck stehenden Fluiden
DE102019000488B4 (de) 2019-01-23 2022-02-10 Hydac Fluidtechnik Gmbh Vorrichtung zum Bereitstellen eines unter einem vorgebbaren Druck stehenden Fluids

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Publication number Publication date
EP4080047A1 (fr) 2022-10-26
EP4080047C0 (fr) 2024-06-05
DE102021002116A1 (de) 2022-10-27

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