EP4127470A1 - Hochdruckpumpe - Google Patents
HochdruckpumpeInfo
- Publication number
- EP4127470A1 EP4127470A1 EP21729834.8A EP21729834A EP4127470A1 EP 4127470 A1 EP4127470 A1 EP 4127470A1 EP 21729834 A EP21729834 A EP 21729834A EP 4127470 A1 EP4127470 A1 EP 4127470A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fluid
- volume flow
- control valve
- flow control
- high pressure
- 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.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims abstract description 76
- 239000000446 fuel Substances 0.000 claims abstract description 30
- 238000001816 cooling Methods 0.000 claims abstract description 28
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 14
- 230000036316 preload Effects 0.000 claims description 11
- 239000002828 fuel tank Substances 0.000 claims description 9
- 238000002347 injection Methods 0.000 claims description 8
- 239000007924 injection Substances 0.000 claims description 8
- 238000007599 discharging Methods 0.000 claims description 5
- 230000001105 regulatory effect Effects 0.000 claims description 4
- 238000002485 combustion reaction Methods 0.000 description 2
- 239000002826 coolant Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0408—Pistons
-
- 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
- F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
-
- 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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
-
- 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
- F04B53/08—Cooling; Heating; Preventing freezing
Definitions
- the present invention relates to a high-pressure pump for raising a pressure level of a fluid, in particular a fuel.
- a fuel to be supplied to a combustion process has a high pressure.
- the usual system pressures for corresponding high-pressure pumps are in the range from 250 to 2500 bar.
- the high-pressure pump has a pump chamber, the volume of which can be reduced by means of a movable piston. If fuel is now introduced into the pump chamber at a low pressure level, the pump chamber is closed and the pump chamber is reduced via a piston movement, this leads to a pressure increase in the fuel present in the pump chamber.
- a corresponding outlet valve ensures that fuel that has reached a desired pressure level is released. If the piston moves from its bottom dead center to its top dead center, that is to say increases the volume of the pump chamber, fuel from the low pressure level is let into the pump chamber and the cycle described begins again from the beginning.
- Piston cooling is implemented via the flow in the low-pressure circuit upstream of the inlet valve.
- the fuel flowing into the pump chamber at intervals is used as a cooling medium for the heat given off by the piston before it passes through the inlet valve.
- a corresponding line routing can be provided which brings the fuel, which is fed to the inlet valve, close to the piston in advance in order to cool it.
- the inlet valve is implemented as a digital inlet valve, so that if no delivery of high pressure is desired, the inlet valve remains open, which means that fuel entering the pump chamber is delivered back into the low-pressure circuit .
- a defined leakage volume is continuously discharged in front of the inlet valve in order to dissipate heat.
- the aim of the present invention is to develop a high-pressure pump of the type described at the beginning so that it can also be operated via a volume flow control. This is achieved with a high pressure pump which has all the features of claim 1.
- a high-pressure pump for raising a pressure level of a fluid, in particular a fuel, which has a movable piston for compressing a pump chamber, an inlet valve for admitting the fluid into the pump chamber, a cooling device for cooling the piston with the aid of upstream of the inlet valve flowing fluid, and comprises a volume flow control valve which is arranged upstream of the cooling device and influences a volume flow of the fluid through the cooling device towards the inlet valve
- bypass throttle which bypasses the volume flow control valve
- a certain fluid flow is generated even in a closed state of the volume flow control valve, which fluid flow can be used to cool the piston.
- the outflow of the fluid flowing into the pump in this way takes place via an outlet throttle which is arranged downstream of the cooling device.
- the inlet valve has a spring preload and is designed to allow the fluid to flow into the pump chamber only when the volume flow control valve assumes an open position.
- the volume flow control valve assumes an open position.
- Spring preloading of the inlet valve ensures that there is no undesired high-pressure delivery of fluid. Small amounts of leakage can occur over the entire service life of the volume flow control valve, but the inlet valve with spring preload can prevent this from leading to an undesired high-pressure delivery of fluid.
- the spring preload is dimensioned in such a way that it does not allow fluid to enter the pump chamber even with small amounts of fluid flowing through the valve (leakage), but rather a certain threshold value must be exceeded for this.
- the inlet valve with spring preload is designed to allow the fluid to flow into the pump chamber only when a certain volume flow of the fluid originating from the volume flow control valve is exceeded, in order to prevent even a slight leakage of the Volume flow control valve leads to an opening of the inlet valve.
- the specific volume flow originating from the volume flow control valve, which leads to an opening of the inlet valve can be at least 10% of the volume flow flowing through the fully open volume flow control valve, preferably at least 5% of the volume flow flowing through the fully open one
- Volume flow control valve be flowing volume flow.
- the cooling device is implemented by a corresponding flow guidance of the fluid in the area of the piston.
- a fluid connection arranged upstream of the inlet valve or the fluid connection between the volume flow control valve and the inlet valve can be routed into the downstream area of the piston so that the fluid flowing in the fluid connection can act as a cooling medium.
- the bypass throttle is connected in parallel to the volume flow control valve and short-circuits it. The bypass throttle can be arranged in such a way that it only short-circuits the volume flow control valve.
- bypass throttle and the return throttle are each designed to allow the passage of a specific volume flow of fluid, which is preferably identical for each of the throttles.
- specific volume flow of the bypass throttle is lower than the specific volume flow of the return flow throttle.
- bypass throttle and the volume flow control valve are connected to a fluid source and the return throttle is preferably connected to a fluid sink.
- the pump further comprises an outlet valve for discharging the fluid from the pump chamber, the outlet valve preferably being provided with a spring preload which ensures that the fluid does not leave the pump chamber until a desired pressure level is reached that is greater than the pressure level upstream of the inlet valve.
- the volume flow control valve is a 2/2-way valve, in particular a 2/2-way solenoid valve, which in a first switching position connects the fluid channels reaching the valve and in a second switching position interrupts the fluid channels reaching the valve.
- any valve upstream of the inlet valve does not have any pressure regulating and / or Has pressure limiting function, preferably the high pressure pump has no pressure regulating and / or pressure limiting valve.
- the high-pressure pump is of the type of a roller tappet pump.
- the movable piston is moved back and forth by the rotation of a drive shaft provided with a cam.
- the interface between the cam and the moving piston assembly is a roller that rolls on the cam.
- the invention further relates to a fuel injection system with a high pressure pump according to one of the preceding variants, wherein fuel delivered from a fuel tank via a fuel pump is supplied to the volume flow control valve and the bypass throttle.
- the return throttle is connected to the fuel tank in order to supply fuel flowing from the high pressure pump to the fuel tank via the return throttle.
- the invention also relates to a work machine with a high-pressure pump according to the variants described above or a corresponding fuel injection system.
- Fig. 1 a schematic structure of the high pressure pump according to the invention.
- the high-pressure pump 1 shows the high-pressure pump 1, which has three connections 11, 12, 13. An inlet connection 11 for supplying fluid with a low pressure level, a return connection 12 for returning fluid with a low pressure level and an outlet connection 13 for discharging fluid with a high pressure level.
- the operating principle of the high pressure pump 1 is based on the repeated back and forth movement of the piston 2 in the cylinder arrangement 10.
- the volume of a pump chamber 3 can be reduced by the movement of the piston 2.
- the pump chamber 3 is connected to both the low-pressure side and the high-pressure side via corresponding valves 4, 8, so that fluid can flow into the pump chamber 3 from the low-pressure side as long as the volume of the pump chamber 3 is at most or less at a corresponding position of the piston 2 is close to its maximum.
- the constant back and forth movement of the piston 2 in the cylinder arrangement 2 leads to a temperature rise caused by friction.
- fluid on the low-pressure side that is to say upstream of the pump chamber 3 is used to absorb and dissipate the heat.
- a fluid guide is provided from the inlet section 11 to the inlet valve 4 in the pump chamber 3, with which the temperature can be derived by moving the piston 2 in the cylinder arrangement 10. This fluid guide, which is directed towards cooling the cylinder arrangement, is referred to as the cooling device 5.
- the fluid guided at the inlet connection 11 can not only flow into the interior of the floch pressure pump 1 via the volume flow control valve 6, but also via the bypass throttle 7, so that even with a so-called “O delivery”, in which no fluid is released on the high pressure side or the volume flow control valve 6 is in its closed position, fluid flows into the pump 1.
- the convection of the inflowing fluid necessary for the removal of heat is achieved by a return throttle 9 which is arranged downstream of the cooling device 5. This return throttle 9 allows the fluid flowing in via the bypass throttle 7 to emerge again from the pump 1, so that the fluid that has been heated in its temperature can flow away.
- the closed volume flow control valve 6 and a non-existent high-pressure fluid output there is a flow of fluid on the low-pressure side, which is used to cool the cylinder arrangement 10 or the piston 2.
- the inlet valve 4 in the pump chamber 3 is a check valve with spring preload
- the spring preload can be dimensioned so that a leak in the volume flow control valve 6 together with the fluid flowing in via the bypass throttle 7 does not allow fluid to flow into the pump chamber 3.
- a high-pressure delivery occurs only when there is a significant increase in pressure upstream of the inlet valve 4 when the volume flow control valve 6 is in its open state.
- the opening pressure of the inlet valve 4 can determine the permissible dynamic pressure in the return. For example, for opening the inlet valve 4, it may be necessary for more than 10%, preferably more than 5%, of the fluid flow that would flow in an open state of the volume flow control valve 6 to flow through the volume flow control valve 6 so that it closes a flowing into the pump chamber 3 comes.
- the outlet valve 8 can also be a check valve with a spring preload. This valve is only opened when a pressure level has been generated in the pump chamber 3 that corresponds to the pressure on the high pressure side. This can be in the range from 250 to 2
- the low pressure range describes a pressure range of less than 15 bar, preferably less than 10 bar and preferably less than 6 bar.
- a low-pressure pump is used which raises the fluid on the low-pressure side to a level of more than 1 bar, preferably more than 3 bar.
- this feed pump for the fluid on the low-pressure side is a fuel pump that conveys fuel from a fuel tank to the high-pressure pump 1.
- the return connection 12 is connected to the fuel tank so that the fluid that has not been brought to the high pressure side can flow back into the fuel tank.
- the high-pressure connection 13 is connected to an injection line, for example a common rail, from which fuel is injected under high pressure into a combustion chamber of an engine.
- a fuel injector can of course also be connected in between.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102020114417.2A DE102020114417A1 (de) | 2020-05-29 | 2020-05-29 | Hochdruckpumpe |
PCT/EP2021/063991 WO2021239785A1 (de) | 2020-05-29 | 2021-05-26 | Hochdruckpumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP4127470A1 true EP4127470A1 (de) | 2023-02-08 |
EP4127470B1 EP4127470B1 (de) | 2024-06-12 |
Family
ID=76269716
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP21729834.8A Active EP4127470B1 (de) | 2020-05-29 | 2021-05-26 | Hochdruckpumpe |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP4127470B1 (de) |
DE (1) | DE102020114417A1 (de) |
WO (1) | WO2021239785A1 (de) |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4236882C1 (de) | 1992-10-31 | 1994-04-21 | Daimler Benz Ag | Kraftstoffeinspritzanlage mit einer Hochdruckpumpe und einer gemeinsamen Versorgungsleitung für alle Einspritzdüsen mit Magnetventilsteuerung |
IT1289796B1 (it) * | 1996-12-23 | 1998-10-16 | Elasis Sistema Ricerca Fiat | Perfezionamenti ad un dispositivo a pompa per l'alimentazione del carburante da un serbatoio ad un motore a combustione interna. |
EP1321663A3 (de) | 2001-12-19 | 2003-07-02 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
DE10318941A1 (de) * | 2003-04-26 | 2004-11-11 | Robert Bosch Gmbh | Kraftstoffsystem für eine Brennkraftmaschine |
DE102005007141B4 (de) | 2005-02-17 | 2006-11-02 | Hydac Electronic Gmbh | Ventil |
DE102005027851A1 (de) | 2005-06-16 | 2006-12-21 | Robert Bosch Gmbh | Kraftstoffeinspritzsystem für eine Brennkraftmaschine |
DE102006013165A1 (de) | 2006-03-22 | 2007-09-27 | Robert Bosch Gmbh | Kraftstoffhochdruckpumpe und Kraftstoffeinspritzsystem für eine Brennkraftmaschine |
DE102009027335A1 (de) * | 2009-06-30 | 2011-01-05 | Robert Bosch Gmbh | Kraftstoffsystem für eine Brennkraftmaschine |
DE102014217388A1 (de) * | 2014-09-01 | 2016-03-03 | Robert Bosch Gmbh | Kraftstoffhochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine |
WO2019206606A1 (en) * | 2018-04-26 | 2019-10-31 | Robert Bosch Gmbh | Pumping unit for feeding fuel, preferably diesel fuel, to an internal combustion engine |
-
2020
- 2020-05-29 DE DE102020114417.2A patent/DE102020114417A1/de active Pending
-
2021
- 2021-05-26 EP EP21729834.8A patent/EP4127470B1/de active Active
- 2021-05-26 WO PCT/EP2021/063991 patent/WO2021239785A1/de unknown
Also Published As
Publication number | Publication date |
---|---|
DE102020114417A1 (de) | 2021-12-02 |
EP4127470B1 (de) | 2024-06-12 |
WO2021239785A1 (de) | 2021-12-02 |
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