WO2019115097A1 - Dispositif d'alimentation en carburant pour carburants cryogéniques - Google Patents

Dispositif d'alimentation en carburant pour carburants cryogéniques Download PDF

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Publication number
WO2019115097A1
WO2019115097A1 PCT/EP2018/080447 EP2018080447W WO2019115097A1 WO 2019115097 A1 WO2019115097 A1 WO 2019115097A1 EP 2018080447 W EP2018080447 W EP 2018080447W WO 2019115097 A1 WO2019115097 A1 WO 2019115097A1
Authority
WO
WIPO (PCT)
Prior art keywords
hollow cylinder
delivery device
fuel delivery
pressure chamber
pump piston
Prior art date
Application number
PCT/EP2018/080447
Other languages
German (de)
English (en)
Inventor
Dirk SCHNITTGER
Friedrich Howey
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
Priority to CN201880079940.0A priority Critical patent/CN111527308B/zh
Priority to EP18800579.7A priority patent/EP3724501B1/fr
Publication of WO2019115097A1 publication Critical patent/WO2019115097A1/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
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F04B15/08—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure the liquids having low boiling points
    • 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
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0245—High pressure fuel supply systems; Rails; Pumps; Arrangement of valves
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/105—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/105—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
    • F04B9/1053—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor one side of the double-acting liquid motor being always under the influence of the liquid under pressure
    • 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
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F04B15/08—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure the liquids having low boiling points
    • F04B2015/081—Liquefied gases

Definitions

  • the invention relates to a fuel delivery device for cryogenic fuels having the features of the preamble of claim 1.
  • a piston pump for cryogenic fuels, in particular for natural gas, with a reciprocating pump piston is known.
  • the pump piston limits a pump working space, which can be filled with liquid natural gas, so that in the pump working space existing liquid natural gas can be acted upon by a lifting movement of the pump piston with high pressure.
  • At the other end of the pump piston limits a coupler space which can be filled with a hydraulic pressure medium to drive the pump piston in a reciprocating motion.
  • an electric, pneumatic or mechanical drive is proposed.
  • Object of the present invention is to provide a fuel delivery device for kryoge ne fuels with a piston pump whose life is increased.
  • the wear in the range of guides and / or seals egg nes reciprocating pump piston of the piston pump should be reduced.
  • the proposed fuel delivery device for cryogenic fuels comprises a piston pump for delivering the cryogenic fuel to high pressure
  • the Kol benpumpe has a reciprocating pump piston
  • the one end egg NEN compression chamber and the other end defines a formed in a hollow cylinder pressure chamber, which can be acted upon by a hydraulic pressure medium is.
  • the pump piston has an annular shoulder for limiting a further pressure chamber formed in the hollow cylinder, which can also be acted upon by the hydraulic pressure medium to return the pump piston.
  • the additional pressure chamber is coupled to a storage volume which is limited by ei ne storage sleeve, which is reciprocally arranged on the hollow cylinder and biased by means of a return spring.
  • the pump piston of the piston pump of the invention Kraftstoffstofördördereinrich device is therefore hydraulically driven.
  • the pump piston moves in the direction of the compression space, ie towards an upper end position in which the volume of Kompres sion space is minimal.
  • the pump piston performs a power stroke in which fuel present in the compression space is compressed.
  • the return of the pump piston is also effected hydraulically, via the hydraulic pressure in the further pressure chamber.
  • the volume of the further pressure chamber is reduced, the volume reduction of the further pressure chamber being compensated by an increase in the volume of the storage volume.
  • the storage volume limiting Spei cherhülse moves in the direction of the return spring, so that it is stretched. Accordingly, the biasing force acting on the storage sleeve increases. If the pump piston has reached its upper end position, the preload force is maximum. The tension before finally leads to the provision of the storage sleeve, wherein the pressure in the storage volume and in the further pressure chamber increases and leads to the provision of Pum penkolbens.
  • the piston pump of the fuel delivery device has a return spring, this is not supported directly on the pump piston, but on the outside arranged on the hollow cylinder storage sleeve.
  • the SpeI cherhülse and the hollow cylinder thus absorb the torsional and lateral forces of the return spring.
  • the pump piston remains unloaded.
  • the support of the return spring on the storage sleeve also has the advantage that due to the available diameter, a particularly large and thus krafti ge spring can be used. In addition, the return spring can easily integrated who the.
  • the storage volume in dependence on the position of the pump piston, preferably in an upper Endla ge of the pump piston, via a connecting channel formed in the hollow cylinder hydraulically connectable to the first pressure chamber.
  • a connecting channel formed in the hollow cylinder hydraulically connectable to the first pressure chamber.
  • a pressure compensation is effected, which leads to the formation of a working stroke of the pump piston limiting hydraulic stop rule.
  • the hydraulic stop prevents a mechanical impact on, so that the load on the pump piston is further reduced. This means that the wear on the pump piston is further reduced or the service life of the piston pump is further increased. Furthermore, the noise reduction during operation of the piston pump is lowered by the hydraulic stop.
  • the upper end position of the pump piston is predetermined via the hydraulic stop.
  • the position of the connecting channel with respect to the pump piston is to be chosen since such that the pump piston releases the connecting channel shortly before reaching the upper end position.
  • the then adjusting pressure equalization leads to the formation of the hydraulic stop, which limits the working stroke of the pump piston be.
  • a check valve is preferably arranged, which prevents a return flow of the hydraulic pressure medium from the storage volume in the first pressure chamber. This means that the connecting channel can only be flowed through in one direction and indeed by the first pressure chamber in the direction of the storage volume or of the further pressure space. This ensures that the Speicherervo lumen and the other pressure chamber for the provision of the pump piston he quired hydraulic pressure can be built up.
  • the storage volume can be connected via a pressure-limiting valve to a leakage line.
  • a pressure relief valve With the help of the pressure relief valve, a maximum hydraulic pressure in the storage volume and in the other pressure chamber can be adjusted. Because of the maximum pressure in the storage volume and in the further pressure chamber, the formation of the hydraulic stop depends, can be taken over the same time influence on the upper end position of the pump piston.
  • the storage volume is therefore connectable depending on the position of the storage sleeve via at least one relief channel formed in the hollow cylinder or via at least one relief opening formed in the storage sleeve with a pressure chamber.
  • the discharge opening in the storage sleeve can be performed in example as a simple radial bore, so that this form of execution can be implemented particularly easily.
  • the storage sleeve on a plurality of relief openings which are further preferably arranged at the same angular distance from each other.
  • the at least one relief opening formed in the storage sleeve is preferably closed. Only at a given stroke of the storage sleeve relative to the hollow cylinder, the discharge Entlas opening is released, so that hydraulic pressure fluid from the Speichervolu men can flow into the low-pressure chamber.
  • the thereby adjusting Druckaus equal between the storage volume and the low-pressure chamber causes a hy lic limit of the stroke of the storage sleeve before it reaches a mechanical impact on. In this way, the wear on the storage sleeve can be reduced. At the same time, the noise emissions can be further reduced.
  • At least one discharge channel is provided in the hollow cylinder instead of the at least one discharge opening in the storage sleeve, the mode of operation is essentially the same. This means that the discharge channel is only released when the storage sleeve has reached a predetermined position.
  • the Speicherervo lumen is connected in dependence on the position of the storage sleeve via an annular gap between the hollow cylinder and the storage sleeve with a low-pressure space.
  • the annular gap creates a circumferential opening of the storage volume to the low-pressure space, so that neither a discharge opening in the storage sleeve, nor a discharge tungskanal in the hollow cylinder is required. This allows a rotationally symmetrical design of at least the storage sleeve, so that their production is simplified.
  • the circumferential annular gap also ensures a smooth and fast flow from the hydraulic pressure fluid from the storage volume in the low-pressure chamber.
  • the low-pressure chamber is connected via a return line and / or via the leakage line with a tank for the hydraulic pressure medium.
  • the low pressure chamber supplied amount of hydraulic pressure fluid is thus not lost to the system.
  • the hydraulic pressure medium may be, for example, an oil, in particular an engine oil.
  • the hollow cylinder preferably has a GE graded outer contour with an annular shoulder. Over the width of the paragraph, the dimension of the storage volume can be specified in the radial direction.
  • the storage sleeve delimiting the storage volume is arranged on the outer diameter of the hollow cylinder.
  • the annular shoulder of the hollow cylinder passes over a cone in ei ne guide surface for the storage sleeve. If the overlap of the storage tube with the guide surface for opening the storage volume is temporarily abandoned over an annular gap around the annular gap, the cone facilitates the return of the storage sleeve or the re-immersion of the hollow cylinder into the storage sleeve.
  • the storage sleeve has a stepped inner contour for limiting the storage volume.
  • the storage sleeve preferably also forms an annular shoulder, which furthermore preferably lies opposite the annular shoulder of the hollow cylinder on the storage volume, where the distance between the two annular shoulders can be changed by a lifting movement of the storage sleeve relative to the hollow cylinder. Due to the stepped th inner contour, the storage sleeve on two different guide diameter. In the region of the larger guide diameter, over which the storage volume is limited in the radial direction, preferably the inner contour of the Speicherhül se end over a cone in an end face over.
  • the cone in turn has the task of facilitating re-immersion of the hollow cylinder in the storage sleeve.
  • the storage volume is therefore preferably formed by an annular space which is arranged concentrically with respect to the pump piston or the first pressure chamber between the hollow cylinder and the storage sleeve.
  • the coupled with the storage volume further pressure chamber is preferably also formed by an annular space GE, which is arranged between the pump piston and the hollow cylinder.
  • FIG. 1 is a schematic longitudinal section through a piston pump of a fiction, contemporary fuel delivery device according to a first preferred embodiment form
  • FIG. 2 shows an enlarged detail of FIG. 1 in the region of the hydraulic drive at the end of a working stroke of the pump piston
  • FIG. 3 shows the detail of FIG. 2 during a suction stroke of the pump piston
  • FIG. 4 is a schematic longitudinal section through a piston pump of a fiction, contemporary fuel delivery according to a second preferred embodiment form, and limited to the area of the hydraulic drive during a power stroke of the pump piston,
  • FIG. 5 shows the detail of FIG. 4 at the end of a working stroke of the pump piston
  • Fig. 6 is a schematic longitudinal section through a piston pump of a fiction, contemporary fuel delivery according to a third preferred embodiment form, and limited to the range of the hydraulic drive during a power stroke of the pump piston
  • Fig. 7 shows the detail of Fig. 6 at the end of the working stroke of the pump piston
  • Fig. 8 is a schematic longitudinal section through a piston pump of a fiction, contemporary fuel delivery device according to a fourth preferred embodiment form, and limited to the range of the hydraulic drive at the end of a power stroke of the pump piston.
  • the fuel delivery device according to the invention shown in FIG. 1 is used to supply an internal combustion engine (not shown) of a motor vehicle with fuel, which is a cryogenic fuel, preferably to natural gas han delt.
  • the fuel delivery device comprises a piston pump 1 for delivering the fuel to high pressure.
  • the fuel is stored in liquid form in a tank (not shown). Via an inlet 27 and a mammal valve 30, the fuel enters a compression chamber 3 of the piston pump 1, which is bounded by a reciprocating pump piston 2.
  • a compression chamber 3 of the piston pump 1 which is bounded by a reciprocating pump piston 2.
  • a power stroke of the pump piston 2 of the presspression space in Kom 3 existing fuel is compressed and fed via a drain 28 a buffer memory (not shown).
  • a check valve 29 is arranged to prevent during a renewed suction stroke of the pump piston 2, a return flow of the fuel into the compression chamber 3.
  • a return line 31 for discharging a leakage amount of the cryogenic fuel is seen before, the space 3 escapes through the seals of the pump piston 2 from the compression.
  • the pump piston 2 of the illustrated piston pump 1 has at its end facing away from the Com pressionsraum 3 a piston portion with an enlarged outer diameter, which is received in a hollow cylinder 4.
  • the pump piston 2 limits two pressure chambers 5, 7, which can be acted upon by a hydraulic pressure medium.
  • the second pressure chamber 7 is bounded by a fancy on the pump piston 2 th annular shoulder 6, which is due to the fürmesserversprungs of the pump piston 2 results. That is, the second pressure chamber 7 is formed as an annular space.
  • the second pressure chamber 7 serves to return the pump piston 2, so that it performs a suction stroke, during which the compression chamber 3, he is again filled with fuel.
  • the second pressure chamber 7 is coupled to a storage volume 8, which is also designed as an annular space and is limited by the hollow cylinder 4 and a lifting sleeve 9 movably guided on the hollow cylinder 4.
  • the hollow cylinder 4 has an outer contour 20 with an annular shoulder 21 which merges into a guide surface 23 for the storage sleeve 9.
  • the storage sleeve 9 in turn has a stepped inner contour 24 for limiting the storage volume 8.
  • the storage sleeve in Rich tion of paragraph 21 of the hollow cylinder 4 is acted upon by the spring force of a return spring 10.
  • the Speicherhül se 9 moves against the spring force of the return spring 10, so that the Speichervolu men 8 increases. This is the case when the pump piston 2 performs a power stroke and thereby reduces the volume of the coupled with the storage volume 8 second pressure chamber 7. The reduction in volume of the second pressure chamber 7 is then compensated by an increase in volume of the storage volume 8 kom. At the same time, the return spring 10 is stretched further. The return spring 10 is maximally tensioned when the storage sleeve 9 abuts against a housing part 32 which, together with the hollow cylinder 4, defines a low-pressure space 17 in which the return spring 10 is accommodated.
  • the pump piston 2 If the pump piston 2 has reached its upper end position (see FIG. 2), it releases a connecting channel 11 in which a check valve 12 is arranged, which allows an inflow of hydraulic pressure fluid into the storage volume 8 and into the second pressure chamber 7. In this way, a pressure equalization in the two pressure chambers 5, 7 is achieved, which leads to the formation of a hydraulic stop. That is, the working stroke of the pump piston 2 is hydraulically limited, whereby the wear on the pump piston 2 is reduced.
  • the return spring 10 presses the storage sleeve 9 in the direction of paragraph 21 of the hollow cylinder 4, so that the storage volume 8 decreases. At the same time the spring force and thus the pressure in the pressure chamber 7, which is still sufficiently high, so that the Pumpenkol ben 2 is reset. Meanwhile prevents in the connecting channel 11 to parent check valve 12 that hydraulic pressure fluid in the first pressure chamber 5 flows back (see Fig. 3).
  • a piston pump 1 shown in Figures 4 and 5 for a fuel delivery device according to the invention is dispensed valve 13 on a Druckbegrenzungsven.
  • Relief of the storage volume 8 is here achieved via several Ent lastungsö réelleen 16, which forms out as radial bores in the storage sleeve 9.
  • the discharge openings 16 are controlled via the stroke of the storage sleeve 9, wherein via the discharge openings 16, a compound of the Speicherervo lumen 8 with the low-pressure chamber 17 can be produced (see FIG. 5).
  • the then an adjusting pressure compensation causes a hydraulic limitation of the stroke of the storage cherhülse 9, so that a mechanical stops the storage sleeve 9 on the housing part 32 is prevented.
  • the reaching into the low pressure chamber 17 amount of hydraulic pressure fluid can be removed via a leakage line 14 and / or a return line 19, so that the pressure in the low-pressure chamber 17 does not rise above a predetermined limit.
  • FIGS. 6 and 7 for a fuel delivery device according to the invention
  • a pressure relief valve 13 is likewise dispensed with.
  • a discharge of the storage volume 8 via a discharge channel 15 is effected, which is formed in the hollow cylinder 4 and - depending on the position of the storage sleeve 9 with respect to the hollow cylinder 4 - the storage volume 8 with the Low pressure chamber 17 connects.
  • the operation is similar to that of the embodiment of FIGS. 4 and 5, so that reference is made to this.
  • FIG. 8 shows a further preferred embodiment of a piston pump 1 for a fuel delivery device according to the invention.
  • the discharge of the storage volume 8 is effected here via an annular gap 18 which, depending on the position of the storage sleeve 9, forms with respect to the hollow cylinder 4 between the storage sleeve 9 and the hollow cylinder 4.
  • the hollow cylinder 4 and the storage sleeve 9 depending Weil a cone 22, 25 on.
  • the cone 22 of the hollow cylinder 4 connects the offset 21 with the guide surface 23 and the cone 25 of the storage sleeve 9 ends at egg ner end face 26.
  • the annular gap 18 ensures a uniform outflow of the hydraulic pressure fluid from the storage volume 8 in the low-pressure chamber 17th
  • the embodiments without pressure relief valve 13 have in common that the return spring 10, the storage sleeve 9 resets until the connection of the Speicherervo lumen 8 with the low-pressure chamber 17 via the discharge openings 16, the discharge channel 15 or the annular gap 18 is closed again.
  • the design is designed so that the existing volume at this time is sufficient to cause the resetting ment of the pump piston 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne un dispositif d'alimentation en carburant destiné à des carburants cryogéniques, comprenant une pompe à piston (1) servant à refouler le carburant cryogénique à haute pression, la pompe à piston (1) présentant un piston de pompe (2) qui peut être animé d'un mouvement alternatif et qui délimite d'une part une chambre de compression (3) et d'autre part une chambre de pression (5), ménagée dans un cylindre creux (4), pouvant être soumise à l'action d'un fluide hydraulique sous pression. Selon l'invention, le piston de pompe (2) présente un épaulement annulaire (6) destiné à délimiter une autre chambre de pression (7) ménagée dans le cylindre creux (4) et pouvant également être soumise à l'action du fluide hydraulique sous pression pour le rappel du piston de pompe (2), cette autre chambre de pression (7) étant reliée à un volume d'accumulation (8) qui est délimité par une douille d'accumulation (9) qui est disposée de manière à pouvoir être animée d'un mouvement alternatif sur le cylindre creux (4) et qui est précontrainte au moyen d'un ressort de rappel (10).
PCT/EP2018/080447 2017-12-11 2018-11-07 Dispositif d'alimentation en carburant pour carburants cryogéniques WO2019115097A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201880079940.0A CN111527308B (zh) 2017-12-11 2018-11-07 用于低温燃料的燃料输送装置
EP18800579.7A EP3724501B1 (fr) 2017-12-11 2018-11-07 Dispositif de pompage de carburant pour des carburants cryogéniques

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017012218.0 2017-12-11
DE102017012218.0A DE102017012218A1 (de) 2017-12-11 2017-12-11 Kraftstofffördereinrichtung für kryogene Kraftstoffe

Publications (1)

Publication Number Publication Date
WO2019115097A1 true WO2019115097A1 (fr) 2019-06-20

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Application Number Title Priority Date Filing Date
PCT/EP2018/080447 WO2019115097A1 (fr) 2017-12-11 2018-11-07 Dispositif d'alimentation en carburant pour carburants cryogéniques

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EP (1) EP3724501B1 (fr)
CN (1) CN111527308B (fr)
DE (1) DE102017012218A1 (fr)
WO (1) WO2019115097A1 (fr)

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CN110131129A (zh) * 2019-05-05 2019-08-16 英嘉动力科技无锡有限公司 一种新型结构低温泵

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CN114962844B (zh) * 2022-04-26 2023-07-21 重庆海浦洛自动化科技有限公司 高粘度介质用蓄能装置及其使用方法

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US6354088B1 (en) * 2000-10-13 2002-03-12 Chart Inc. System and method for dispensing cryogenic liquids
US7293418B2 (en) * 2001-11-30 2007-11-13 Westport Power Inc. Method and apparatus for delivering a high pressure gas from a cryogenic storage tank
EP2541062A1 (fr) 2011-06-29 2013-01-02 Westport Power Inc. Pompe cryogène
DE102014001193A1 (de) * 2013-02-27 2014-08-28 Caterpillar Inc. Hydraulische Entlastung und Schaltlogik für kryogenes Pumpsystem
US20170037836A1 (en) * 2015-08-06 2017-02-09 Caterpillar Inc. Cryogenic Pump for Liquefied Natural Gas

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CN101691854A (zh) * 2009-10-14 2010-04-07 同济大学 一种新型燃料加压泵及加压系统
CN104279135B (zh) * 2013-07-11 2018-10-16 西港能源有限公司 低压低温泵组件
DK179219B1 (en) * 2016-05-26 2018-02-12 Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland Fuel or lubrication pump for a large two-stroke compression-ignited internal combustion engine

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Publication number Priority date Publication date Assignee Title
US6354088B1 (en) * 2000-10-13 2002-03-12 Chart Inc. System and method for dispensing cryogenic liquids
US7293418B2 (en) * 2001-11-30 2007-11-13 Westport Power Inc. Method and apparatus for delivering a high pressure gas from a cryogenic storage tank
EP2541062A1 (fr) 2011-06-29 2013-01-02 Westport Power Inc. Pompe cryogène
DE102014001193A1 (de) * 2013-02-27 2014-08-28 Caterpillar Inc. Hydraulische Entlastung und Schaltlogik für kryogenes Pumpsystem
US20170037836A1 (en) * 2015-08-06 2017-02-09 Caterpillar Inc. Cryogenic Pump for Liquefied Natural Gas

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110131129A (zh) * 2019-05-05 2019-08-16 英嘉动力科技无锡有限公司 一种新型结构低温泵

Also Published As

Publication number Publication date
CN111527308A (zh) 2020-08-11
EP3724501A1 (fr) 2020-10-21
DE102017012218A1 (de) 2019-06-13
CN111527308B (zh) 2022-07-19
EP3724501B1 (fr) 2021-11-03

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