WO2017215839A1 - Pompe de refoulement pour carburants cryogéniques et système de refoulement de carburant - Google Patents

Pompe de refoulement pour carburants cryogéniques et système de refoulement de carburant Download PDF

Info

Publication number
WO2017215839A1
WO2017215839A1 PCT/EP2017/060873 EP2017060873W WO2017215839A1 WO 2017215839 A1 WO2017215839 A1 WO 2017215839A1 EP 2017060873 W EP2017060873 W EP 2017060873W WO 2017215839 A1 WO2017215839 A1 WO 2017215839A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
fuel
feed
inlet
pressure
Prior art date
Application number
PCT/EP2017/060873
Other languages
German (de)
English (en)
Inventor
Andreas Kellner
Falko Bredow
Frank Zehnder
Dirk SCHNITTGER
Andreas Beiter
Marc Oliver Roehner
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2017215839A1 publication Critical patent/WO2017215839A1/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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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 feed pump for cryogenic fuels after the
  • the invention relates to a
  • a feed pump for cryogenic fuels according to the preamble of the claim
  • the known feed pump serves to convey fuel from a tank container in the direction of
  • Feed pump arranged, reciprocating piston acts.
  • a check valve is arranged on the pressure-side outlet of the pump chamber of the feed pump, which ensures that the funded via the output or the pressure port in the direction of the heater at each stroke by the piston fuel can not then flow back into the pump chamber.
  • the known delivery pump is at a constant
  • the feed pump for cryogenic fuels having the features of claim 1 has the advantage that in a relatively simple manner, the delivery rate of the feed pump to the actual fuel demand even with a rigid coupling of the feed pump, especially when the feed pump is connected to an internal combustion engine, adjusted can. Under a rigid coupling is understood that a variable speed of the drive in a possibly with the interposition of a reduction gear
  • the invention is based on the idea of influencing the flow rate at the inlet of the pump chamber by means of an electrically operable valve. Thereby, it is possible to control the amount of fuel flowing into the pump space during the movement of the pump element during the suction movement. Also, a delayed closing of the valve acting as a check valve can be made possible to reduce the flow rate or to allow a time-limited backflow in the direction of the suction side. As a result, for example, with a low requirement for fuel, the possibility is opened up to leave the valve at least temporarily in an open position. This has the consequence that when a movement of the pump element in the pump chamber previously infused fuel is ejected again at least partially via the suction port from the pump chamber.
  • an electrically operable valve has the particular advantage that it can be implemented with little device complexity and works quickly or reliably with a high clock frequency.
  • Pump chamber also makes it possible, the inlet and the outlet of the pump chamber in a common portion of the pump chamber
  • valve closes the inlet of the pump chamber
  • Has closing element the force applied by means of a spring element in the de-energized state of the electric valve, the closing element in the position releasing the inlet.
  • the closing element is arranged within the pump chamber in register with the inlet and is connected via a coupling rod in operative connection with an armature.
  • the closing element and the coupling rod are formed as separate elements, i. that there is only a contact between the two components, such that the coupling rod, the closing element only in the direction of his
  • the electrically actuated valve is adapted to the inlet during movement of the pump element in the direction of the inlet in the opening direction to press.
  • this means that the valve is the inlet during a compression phase or the compression movement of the
  • Pump element keeps open, as long as this is its electromagnetic drive allows. As long as the valve has not yet closed the inlet, it is possible that fuel flows out of the inlet during a movement of the pump element in the direction of the inlet and does not reach the pressure port or in the direction of a heating device. The sooner the closing movement of the valve begins, the greater is the amount of fuel delivered per delivery stroke in the direction of the pressure connection of the delivery pump.
  • the invention also includes a fuel delivery system for a gas powered vehicle using a feed pump of the invention.
  • the feed pump is used to compress the fuel to the required system pressure, for example, to a pressure of the fuel, which is several hundred bar.
  • the fuel delivery system is characterized in that the feed pump is preceded by a prefeed pump, which compresses the fuel at the suction port of the feed pump to a prefeed pressure at which the fuel is not yet evaporated.
  • Fuel feed system has the advantage that the (high-pressure) feed pump according to the invention can be arranged in a region relatively far away from the tank container, for example at an interface on the internal combustion engine for driving the feed pump. In addition, this reduces a transmission of the heat of the drive of the feed pump in the fuel in the tank container.
  • a particularly simple drive of the feed pump is made possible when the fuel feed system has a mechanical coupling with an internal combustion engine, which serves to drive the feed pump.
  • Interposition of a transmission takes place, for example, increases or decreases the speed of the internal combustion engine.
  • Fig. 1 is a simplified representation of a fuel delivery system for a
  • Fig. 2 shows a detail of a feed pump, as in the
  • Fuel supply system of FIG. 1 is used, in an enlarged view.
  • a fuel delivery system 100 for cryogenic fuel 1 is shown.
  • the fuel 1 is natural gas or hydrogen which has been cooled down in a tank container 2 to a temperature of, for example, -10 ° C. or less so that it is below a filling level 3 in liquid form.
  • the fuel 1 is in a gaseous state.
  • the tank container 2 preferably consists of an inner tank accommodating the fuel 1, which is evacuated from an outer shell to form an evacuated tank
  • a low-pressure pump 4 As
  • Pre-feed pump preferably below the filling level 3, arranged.
  • the drive 5 of the low pressure pump 4 is disposed within the tank 2.
  • On the pressure side of the low-pressure pump 4 are a
  • shut-off valve 6 and a pressure relief valve 7 is arranged.
  • the shut-off valve 6 is closed in the de-energized state, and the pressure limiting valve 7 serves to prevent damage to the low-pressure delivery pump 4 in the event of a defective shut-off valve 6.
  • the pressure side of the low-pressure feed pump 4 delivers the fuel 1 (with the shut-off valve 6 open) into a supply line 8.
  • a feed pump 10 is arranged as a high-pressure pump.
  • the feed pump 10 is supplied on the suction side of the fuel 1 of the low-pressure feed pump 4 and is connected on the pressure side to a particular designed in the form of a heat exchanger heater 15, in turn, on the side facing away from the feed pump 10
  • Intermediate circuit of a buffer memory 17 and a pressure control valve 18 is connected by way of example with a rail 16.
  • the rail 16 is connected, by way of example, to a plurality of gas valves 20, which serve to convey the fuel initially conveyed by the feed pump 10 into the heating device 15, which is heated by the heating device 15, into the combustion chamber of a not-shown fuel
  • the internal combustion engine is part of a gas-powered vehicle.
  • the pressure of the fuel 1 in the tank container 2 is approximately between 3 bar and 15 bar
  • the pressure on the suction side of the feed pump 10 is caused by the pressure increase by the
  • Low pressure feed pump 4 approximately between 10bar and 20bar, while the pressure of the fuel 1 at the pressure side of the feed pump 10 may be up to 60bar, for example.
  • the feed pump 10 has a systemic limit 21 shown only symbolically.
  • the fuel 1 passes through a suction port 22 via the
  • System boundary 21 and flows in the region of a pressure port 23 from the system boundary 21 in the direction of the heater 15 from.
  • System boundary 21 is under formation of a fuel 1 filled
  • a cylinder 26 arranged or formed.
  • a longitudinal bore 27 is formed, in which a pump element 28 in the form of a high-pressure pump piston 29 in the direction of the double arrow 31 along a longitudinal axis of the longitudinal bore 37 is arranged back and forth.
  • the high-pressure pump piston 29 is connected via a piston rod 32 and a connecting rod 33 connected to the piston rod 32 with a crankshaft 35, which in turn is coupled to a drive 38 arranged with an example outside the system boundary 21 arranged transmission 37.
  • the drive 38 is in particular the internal combustion engine whose crankshaft, for example, also for driving the crankshaft 35 of the Feed pump 10 is used.
  • the crankshaft 35 together with the connecting rod 33, that the rotational movement of the crankshaft 35 in the direction of the arrow 39 in the above-mentioned reciprocating motion of the connecting rod 32 and the
  • High-pressure pump piston 29 is transmitted in the direction of the double arrow 31.
  • the longitudinal bore 27 forms within the cylinder 26 u.a. a cylindrical pump chamber 40, which has on the side facing away from the piston rod 32 side of the high-pressure pump piston 29 via a longitudinal bore 41 connection to a transverse bore 42.
  • the transverse bore 42 is at least indirectly connected to the suction port 22.
  • the longitudinal bore 41 is of a
  • Coupling rod 44 interspersed with radial spacing, which within the
  • Closing element 45 is part of an electrically actuatable valve 50.
  • Coupling rod 44 is connected on the side facing away from the closing element 45 with an armature 51 which cooperates with a magnet 51 radially surrounding the armature 51. Furthermore, the armature 51 is arranged in operative connection with a compression spring 53, the armature 51 and thus also the closing element 45 in the direction of the high-pressure pump piston 29th
  • Transition region of the longitudinal bore 27 to the longitudinal bore 41 (which has a smaller diameter than the longitudinal bore 27) can bear sealingly. This concern or sealing can take place even when energized solenoid 32 when the pressure prevailing in the pump chamber 40 hydraulic pressure is greater than the opening force of the compression spring 53 (together with the pressure prevailing in the longitudinal bore 41 hydraulic pressure).
  • Closing element 45 is moved by abutting contact with the coupling rod 44 in the direction of the high pressure pump piston 29 and thus on the longitudinal bore 41st
  • Fuel 1 can flow into the pump chamber 40.
  • the longitudinal bore 41 forms thus on the pump chamber 40 side facing an inlet 58 from.
  • an outlet 59 with a high-pressure valve 60 is formed in the pump chamber 40.
  • the high pressure valve 60 is as
  • Non-return valve formed and prevents backflow of fuel 1 in the direction of the pump chamber 40. Furthermore, it is preferably provided that the high pressure valve 60 opens only when a certain minimum pressure is exceeded.
  • the fuel 1 reaches the pressure connection 23 at least indirectly via the outlet 59. Both the inlet 58 and the outlet 59 are arranged in a partial region 61 of the pump chamber 40, into which the
  • High-pressure pump piston 29 does not get in his reciprocation.
  • valve 50 within the feed pump 10 is explained as follows: When not actuated valve 50 and not energized solenoid 52, the closing element 45 is pressed by the spring force of the compression spring 53 in the inlet 58 releasing position. As a result, in a (suction) movement of the high-pressure pump piston 29 from the right in FIG. 1 side in the direction of the left side reaches up to the reversal point of the
  • High-pressure pump piston 29 fuel 1 via the longitudinal bore 41 in the pump chamber 40.
  • a closing of the inlet 58 is prevented by the compression spring 53, so that fuel 1 from the inlet 58 can flow back in the direction of the suction port 22, since at the same time the high pressure valve 60 does not open due to the low pressure increase.
  • the valve 50 is not actuated or the solenoid coil 52 is not energized, no fuel 1 is thus conveyed in the direction of the pressure connection 23 or the heating device 15.
  • Reversing point of the high-pressure pump piston 29 is activated or energized after the suction of fuel 1 in the pump chamber 40, the closing element 45 can move against the spring force of the compression spring 53 in its closing the inlet 58 position so that it acts as a check valve. This will fuel 1 in the subsequent movement of the
  • High-pressure pump piston 29 is energized from the side facing away from the inlet 58 in the direction of the inlet 58, so first fuel 1 during the movement of the high-pressure pump piston 29 in the direction of the inlet 58 from the inlet 58 is conveyed out until the closure member 45 closes or seals the inlet 58 , From this point on, the fuel 1 is conveyed via the outlet 59 in the direction of the pressure connection 23 or the heating device 15.
  • the delivery quantity of the fuel 1 during a working stroke of the high-pressure pump piston 29 can thus be adjusted as needed.
  • the delivery pump 10 described so far can be modified or modified in many ways, without departing from the spirit. So it is particularly conceivable to form the valve 50 with reverse direction of action. In this case, the inlet 58 is kept open in the energized state of the solenoid coil 52 and closed in the de-energized state by the compression spring 53, the inlet 58 by the closing element 45.

Landscapes

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

Abstract

L'invention concerne une pompe de refoulement (10) pour carburants cryogéniques (1), comprenant un raccord d'aspiration (22) qui peut être relié au moins indirectement à un réservoir (2) de carburant (1), un raccord de pression (23) qui peut être relié de préférence à un dispositif de chauffage (15), un élément de pompe (28) pouvant être actionné par un entraînement (38) pour comprimer le carburant (1) dans une chambre de pompe (40), la chambre de pompe (40) étant reliée au raccord d'aspiration (22) par le biais d'une entrée (58) et au raccord de pression (23) par le biais d'une sortie (59).
PCT/EP2017/060873 2016-06-16 2017-05-08 Pompe de refoulement pour carburants cryogéniques et système de refoulement de carburant WO2017215839A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016210752.6A DE102016210752A1 (de) 2016-06-16 2016-06-16 Förderpumpe für kryogene Kraftstoffe und Kraftstofffördersystem
DE102016210752.6 2016-06-16

Publications (1)

Publication Number Publication Date
WO2017215839A1 true WO2017215839A1 (fr) 2017-12-21

Family

ID=58739015

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2017/060873 WO2017215839A1 (fr) 2016-06-16 2017-05-08 Pompe de refoulement pour carburants cryogéniques et système de refoulement de carburant

Country Status (2)

Country Link
DE (1) DE102016210752A1 (fr)
WO (1) WO2017215839A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110805507A (zh) * 2018-08-06 2020-02-18 罗伯特·博世有限公司 用于低温燃料的燃料输送装置的阀装置和燃料输送装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1982003337A1 (fr) * 1981-04-03 1982-10-14 Inc Cryomec Systeme de decharge pour cryopompes
DE19644915A1 (de) * 1996-10-29 1998-04-30 Bosch Gmbh Robert Hochdruckpumpe
US5996472A (en) * 1996-10-07 1999-12-07 Chemical Seal And Packing, Inc. Cryogenic reciprocating pump
EP2541062A1 (fr) 2011-06-29 2013-01-02 Westport Power Inc. Pompe cryogène

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1982003337A1 (fr) * 1981-04-03 1982-10-14 Inc Cryomec Systeme de decharge pour cryopompes
US5996472A (en) * 1996-10-07 1999-12-07 Chemical Seal And Packing, Inc. Cryogenic reciprocating pump
DE19644915A1 (de) * 1996-10-29 1998-04-30 Bosch Gmbh Robert Hochdruckpumpe
EP2541062A1 (fr) 2011-06-29 2013-01-02 Westport Power Inc. Pompe cryogène

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110805507A (zh) * 2018-08-06 2020-02-18 罗伯特·博世有限公司 用于低温燃料的燃料输送装置的阀装置和燃料输送装置

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Publication number Publication date
DE102016210752A1 (de) 2017-12-21

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