US20130022484A1 - High-pressure pump - Google Patents
High-pressure pump Download PDFInfo
- Publication number
- US20130022484A1 US20130022484A1 US13/579,190 US201113579190A US2013022484A1 US 20130022484 A1 US20130022484 A1 US 20130022484A1 US 201113579190 A US201113579190 A US 201113579190A US 2013022484 A1 US2013022484 A1 US 2013022484A1
- Authority
- US
- United States
- Prior art keywords
- pump
- inlet valve
- valve
- pressure
- pressure pump
- 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.)
- Abandoned
Links
- 239000000446 fuel Substances 0.000 claims abstract description 38
- 238000002347 injection Methods 0.000 claims abstract description 5
- 239000007924 injection Substances 0.000 claims abstract description 5
- 238000002485 combustion reaction Methods 0.000 claims abstract description 4
- 230000005291 magnetic effect Effects 0.000 claims description 11
- 238000013016 damping Methods 0.000 claims description 8
- 239000003302 ferromagnetic material Substances 0.000 claims description 3
- 230000008901 benefit Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 230000004907 flux Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000004913 activation Effects 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 2
- 230000000712 assembly Effects 0.000 description 2
- 238000000429 assembly Methods 0.000 description 2
- 239000004020 conductor Substances 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000005294 ferromagnetic effect Effects 0.000 description 2
- 238000011010 flushing procedure Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000003321 amplification Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000004137 mechanical activation Methods 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
Images
Classifications
-
- 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
- F02M59/102—Mechanical drive, e.g. tappets or cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/3809—Common rail control systems
- F02D41/3836—Controlling the fuel pressure
- F02D41/3845—Controlling the fuel pressure by controlling the flow into the common rail, e.g. the amount of fuel pumped
-
- 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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
-
- 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
- F02M59/20—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
- F02M59/367—Pump inlet valves of the check valve type being open when actuated
-
- 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
- F02M59/46—Valves
- F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating 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
- F02M59/44—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
- F02M59/48—Assembling; Disassembling; Replacing
-
- 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
- F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve 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
- 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
- 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
- F04B53/007—Cylinder heads
-
- 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
-
- 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
- F04B53/22—Arrangements for enabling ready assembly or disassembly
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
- F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
Definitions
- the invention concerns a high-pressure pump, in particular a radial or in-line piston pump.
- the invention concerns in particular the field of fuel pumps for fuel injection systems of air-compressing, auto-ignition internal combustion engines.
- the high-pressure pump can however also be used as a piston pump to deliver other suitable fluids.
- DE 195 15 191 A1 discloses a high-pressure fuel pump.
- the high-pressure fuel pump has a cylinder, the upper part of which lies open towards the outside of the head cover which is part of the engine housing. The remaining segment of the high-pressure fuel pump is accommodated in a housing hole in the head cover.
- a pump cam is mounted on a valve camshaft to drive an intake/exhaust valve and drives the high-pressure fuel pump. As the time behavior with which the pressurized fuel is expelled is controlled by activation of a solenoid valve, the accuracy with which the fuel delivery is controlled is also improved.
- the high-pressure fuel pump disclosed in DE 195 15 191 A1 is a pump choked on the suction side which has several disadvantages.
- the disadvantages are high noise, poor controllability and the occurrence of mechanical vibrations due to cavitations occurring in the supply lines to the inlet valves. Pressure waves between a feed metering unit and the suction valve have an unfavorable effect on the function.
- the high-pressure pump according to the invention has the advantage that an improved design is achieved in which in particular a metered fuel feed and compact design are possible. In particular no feed metering unit or similar is required, leading to a substantial cost reduction in production.
- inlet valve into the cylinder head allows a very small construction size. This also applies for very high pressures, for example of 300 MPa (3000 bar) as conceivable for application on trucks.
- the inlet valve is formed as a magnetically controllable inlet valve. Furthermore it is advantageous that the inlet valve is fixed to the cylinder head by means of a screw plug screwed into the cylinder head, and that the screw plug is formed of a ferromagnetic material. As a result the screw plug can serve as a magnetic conductor which improves the efficiency of the magnetic circuit and allows a high magnetic force.
- a magnet coil to be provided, that the inlet valve can be controlled via current flowing through the magnet coil, and that the magnet coil can be cooled by fuel that can be transferred via the inlet valve to the pump working chamber.
- cooling of the magnet coil and further elements of the magnetic circuit can be achieved by flushing with the fuel.
- the inlet valve has a valve body and a valve tappet co-operating with the valve body to form a seal seat, wherein the valve tappet lies on the cylinder head, wherein a magnetically activatable solenoid plunger is provided and wherein the solenoid plunger carries the valve tappet with it on mechanical activation to open the seal seat formed between the valve body and the valve tappet.
- the magnetic force to activate the inlet valve can be generated via the solenoid plunger, wherein the screw plug advantageously serves as a magnetic conductor.
- the inlet valve is here preferably closed when the magnet coil is switched without current. If current flows through the magnet coil of the magnet and the pump piston is for example at the top dead center, then the inlet valve opens.
- the inlet valve On full filling, the inlet valve is preferably open until the bottom dead center of the pump piston. It is furthermore advantageous here that an adjustment shim is provided which serves to specify a working air gap and a residual air gap for the solenoid plunger. This allows a modular design wherein by fitting of a suitable adjustment shim, adaptation is possible to the respective application of the high-pressure pump. This expands the application range of the high-pressure pump, wherein simple adaptation and largely identical design of the high-pressure pump are possible.
- a controller which controls the inlet valve as a function of movement of the pump piston of the pump assembly.
- the controller to reduce the filling of the pump working chamber of the pump assembly, shortens the control time at its end so that the inlet valve is closed before the pump piston reaches the bottom dead center, or extends the control time at its end so that the inlet valve is closed after the pump piston reaches a bottom dead center.
- the control time can be reduced so that the inlet valve is closed again before the pump piston reaches the bottom dead center, which reduces the quantity of fuel flowing into the pump working chamber.
- the injector valve is only closed after the reaching of the bottom dead center, whereby the fuel transferred to the pump working chamber is returned partly via the inlet valve in the opposite direction by the movement of the pump piston.
- the pressure fluctuations on the low pressure side are reduced.
- no cavities occur in the working cylinder.
- the advantageous variant may be selected specially depending on the application.
- the control time is shortened at its start so that the inlet valve is opened only after the pump piston reaches a top dead center. Thus the inlet valve is not opened immediately after the top dead center, so that the quantity of fuel flowing into the pump working chamber is also reduced.
- a suitable combination of control methods can be performed by the controller.
- control time can be shortened both at its start and at its end.
- pressure fluctuations can be influenced positively with regard to amplitude and frequency by one or more chokes connected before the inlet valve.
- quantity regulation can be positively influenced. In this way the noise behavior, which can be unfavorably affected by pressure fluctuations in the low pressure, can be improved.
- the inlet valve is preferably fitted with a closing spring with a high spring pretension to achieve a high closing dynamic.
- FIG. 1 a high-pressure pump in an extract, schematic, axial cross section view corresponding to one embodiment example of the invention.
- FIG. 1 shows a high-pressure pump 1 in an extract, schematic, axial cross section view corresponding to one embodiment example of the invention.
- the high-pressure pump 1 can in particular be designed as a radial or in-line piston pump.
- the high-pressure pump 1 is particularly suitable as a fuel pump for fuel injection systems of air-compressing, auto-ignition internal combustion engines.
- a preferred use of the high-pressure pump 1 lies in a fuel injection system with a fuel distribution rail which stores diesel fuel under high pressure.
- the high-pressure pump 1 according to the invention is however also suitable for other applications.
- the high-pressure pump can be used as a piston pump to deliver suitable fluids, in particular fluids other than fuel.
- the high-pressure pump 1 has a pump housing which is mounted on a cylinder head 2 .
- the cylinder head 2 has a shoulder 3 which protrudes into a bore in the pump housing.
- a cylinder bore 4 in which a pump piston 5 of a pump assembly 6 is guided along an axis 7 .
- the high-pressure pump 1 also has a drive shaft 8 on which is provided a cam 9 .
- the cam 9 can here also be designed as a multiple cam or as an eccentric segment of the drive shaft 8 .
- the drive shaft 8 with the cam 9 rotates about a rotary axis 10 .
- an active connection 11 which is illustrated by the double arrow 11 .
- an actuation force can be transferred by the cam 9 to the pump piston 5 .
- a return of the pump piston 5 can take place via a suitable tappet spring.
- the pump assembly 6 can be driven by the cam 9 of the drive shaft 8 .
- further pump assemblies can also be driven by the cam 9 .
- Also on the drive shaft 8 can be provided further cams which serve to drive further pump assemblies.
- a high-pressure pump 1 can thus be constructed as a radial or in-line piston pump.
- the pump piston 5 in the cylinder bore 4 delimits a pump working chamber 12 .
- a supply channel 13 serves to supply fuel which is delivered therein by a pre-delivery pump.
- a first choke 14 and a second choke 15 are provided in the supply channel 13 .
- the supply channel 13 leads into a low pressure chamber 16 which is formed by a recess 17 in the cylinder head 2 .
- the high-pressure pump 1 has an inlet valve 20 .
- the low pressure chamber 16 is here part of the inlet valve 20 .
- the inlet valve 20 is integrated in the cylinder head 2 .
- the inlet valve 20 is arranged in the recess 17 of the cylinder head 2 .
- the recess 17 is here closed by a screw plug 21 .
- the screw plug 21 acts via a valve part 22 on a valve body 23 .
- the screw plug 21 is screwed into the cylinder head 2 and through this presses the valve body 23 against a contact surface 24 formed on the cylinder head 2 .
- the screw plug 21 , valve part 22 and valve body 23 of the inlet valve 20 are thus fixed in a stationary manner.
- the screw plug 21 and valve part 22 are preferably formed of ferromagnetic material.
- valve tappet 25 In the valve body 23 is guided a valve tappet 25 .
- the valve tappet 25 co-operates with a valve seat surface 26 formed on the valve body 23 to form a seal seat.
- a valve spring 27 presses the valve tappet 25 against the valve seat surface 26 .
- the valve spring 27 here acts via a valve element 28 and an adjustment shim 29 on a rotor 30 .
- the rotor 30 is formed as a solenoid plunger 30 .
- the solenoid plunger 30 is connected with the valve tappet 25 .
- the valve tappet 25 is pressurized by the pretension of the valve spring 27 .
- the valve tappet 25 , valve element 28 , adjustment shim 29 and solenoid plunger 30 of the inlet valve 20 are mobile elements which are moved to open the inlet valve 20 on control of the inlet valve 20 .
- the inlet valve 20 also has a magnet 31 with a magnet coil 32 .
- the magnet coil 32 is electrically connected via electrically conductive contact pins 33 , 34 with pins 35 , 36 of a plug 37 .
- the plug 37 here allows connection with a control unit 38 .
- the control unit 38 in this embodiment example serves as a controller 38 .
- the controller 38 can also be integrated in a central control unit.
- the control unit 38 is connected with a rotary angle sensor 39 which detects the momentary rotation angle of the drive shaft 8 and emits this to the control unit 38 . Via the rotary angle detected, there is a direct connection to the momentary position of the pump piston 5 .
- the magnet coil 32 Current flowing through the magnet coil 32 generates a magnetic flux. This magnetic flux is emitted by the magnet 31 wherein an amplification is possible via the ferromagnetic screw plug 21 . The magnetic flux also runs via the valve part 22 , the solenoid plunger 30 and where applicable further ferromagnetic elements back to the screw plug 21 . Between the solenoid plunger 30 and the valve part 22 there is a gap 40 .
- the gap 40 firstly allows displaceability of the solenoid plunger 30 and thus an adjustment of the valve tappet 25 to activate the inlet valve 20 . Secondly at least one rest air gap remains as gap 40 in order to avoid, in activated state, a so-called magnetic adhesion effect of the solenoid plunger 30 on the valve part 22 .
- the force of the valve spring 27 can initiate a closure of the inlet valve 20 largely without distortion.
- the maximum size of the gap 40 is specified by the sum of the desired working air gap and the residual air gap. Adjustment of the residual air gap and working air gap is possible by suitable selection of valve element 28 and adjustment shim 29 .
- the thickness of the adjustment shim 29 can pre-specify the desired working air gap. The thickness of the adjustment shim 29 thus specifies the stroke of the valve tappet 25 .
- inlet valve 20 By actuating inlet valve 20 , fuel can thus be guided from the low-pressure chamber 16 to the pump working chamber 12 . Activation of the inlet valve 20 here takes place during a suction stroke of the pump piston 5 . During the delivery stroke of the pump piston 5 , the inlet valve 20 is preferably closed. Thus fuel under high pressure is delivered via outlet valve 41 —which can be designed as a directional or non-return valve 41 —into a high-pressure line 42 .
- the high-pressure line 42 is for example connected with a fuel distribution rail.
- the inlet valve 20 is opened at approximately the top dead center of a pump piston 5 and closed at the bottom dead center of pump piston 5 , a full filling of the pump working chamber 12 can be achieved.
- the inlet valve 20 can be controlled by the controller 38 irrespective of the stroke or momentary position of pump piston 5 during the suction phase. This allows also a partial filling of the pump working chamber 12 . There are several possibilities for this which can be combined where applicable.
- One possibility is to reduce the control time of the inlet valve 20 so that the inlet valve 20 is closed again before the pump piston 5 reaches the bottom dead center.
- the control time can also be extended beyond the reaching of the bottom dead center.
- the inlet valve 20 is thus only closed after pump piston 5 reaches the bottom dead center so that part of the fuel is delivered back from the pump working chamber 12 during the stroke of the pump piston 5 in the direction back through the inlet valve 20 .
- the other part of the fuel is delivered then via the high-pressure line 42 .
- the quantity of fuel delivered via the high-pressure line 42 per pump stroke is thus reduced.
- a further possibility of achieving a partial filling is that the inlet valve is not opened immediately after pump piston 5 reaches the top dead center. This achieves a certain idle stroke of the pump piston 5 so that the entirety of fuel flowing into the pump working chamber 12 via the opening cross section of the opened seat seal is thus reduced.
- the pressure fluctuations can be reduced with regard to amplitude and frequency and the quantity control can be reduced.
- the chokes here allow a large partial reflection and slight damping of pressure and attenuation waves.
- Damping volumes allow a lower partial reflection and greater damping of the pressure and attenuation waves. This is dependent on the geometric design of the respective damping volume.
- the reflected waves can inter alia make contact again on an opening process of the inlet valve 20 and thus further influence the filled mass in the pump working chamber, which can lead to delivery fluctuations of the high-pressure pump.
- damping volumes and chokes 14 , 15 in the supply channel 13 and by matching these such pressure waves can be reduced so far that a constant delivery of the high-pressure pump 1 is guaranteed within a certain tolerance range.
- the design and dimensioning here depend on the area of application of the high-pressure pump 1 and the connection to the pre-delivery pump.
- an intake valve 20 can be produced which is closed in the unpowered state.
- This inlet valve 20 is integrated in the cylinder head 2 .
- the solenoid plunger principle can be utilized here so that rapid opening and closing of the intake valve 20 can be achieved.
- the suction choking can be shifted into the working cylinder with deliberate utilization of an air exhalation.
- the necessary dynamic can be guaranteed by one or more connecting bores.
- a sufficiently high closing dynamic can be achieved via a correspondingly high spring pretension of valve spring 27 .
- the cooling of the magnet 31 with the magnet coil 32 can be achieved by flushing with fuel.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fuel-Injection Apparatus (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
A high-pressure pump (1), which serves in particular as a radial or inline piston pump for fuel injection systems of air-compressing, auto-ignition internal combustion engines, comprises a cylinder head (2) and a pump assembly (6). Here, the cylinder head (2) has a cylinder bore (4) in which a pump piston (5) of the pump assembly (6) is guided. Here, the pump piston (5) delimits, in the cylinder bore (4), a pump working chamber (12). Also provided is an inlet valve (20) which is integrated into the cylinder head (2) and via which fuel can be conducted into the pump working chamber (12). Metering of the fuel conducted into the pump working chamber (12) can be achieved by actuation of the inlet valve (20). Here, full charging of the pump working chamber (12) may take place. It is however also possible for partial charging of the pump working chamber (12) to be achieved by means of suitable actuation of the inlet valve (20).
Description
- The invention concerns a high-pressure pump, in particular a radial or in-line piston pump. The invention concerns in particular the field of fuel pumps for fuel injection systems of air-compressing, auto-ignition internal combustion engines. The high-pressure pump can however also be used as a piston pump to deliver other suitable fluids.
- DE 195 15 191 A1 discloses a high-pressure fuel pump. The high-pressure fuel pump has a cylinder, the upper part of which lies open towards the outside of the head cover which is part of the engine housing. The remaining segment of the high-pressure fuel pump is accommodated in a housing hole in the head cover. A pump cam is mounted on a valve camshaft to drive an intake/exhaust valve and drives the high-pressure fuel pump. As the time behavior with which the pressurized fuel is expelled is controlled by activation of a solenoid valve, the accuracy with which the fuel delivery is controlled is also improved.
- The high-pressure fuel pump disclosed in DE 195 15 191 A1 is a pump choked on the suction side which has several disadvantages. The disadvantages are high noise, poor controllability and the occurrence of mechanical vibrations due to cavitations occurring in the supply lines to the inlet valves. Pressure waves between a feed metering unit and the suction valve have an unfavorable effect on the function.
- The high-pressure pump according to the invention has the advantage that an improved design is achieved in which in particular a metered fuel feed and compact design are possible. In particular no feed metering unit or similar is required, leading to a substantial cost reduction in production.
- In contrast to high-pressure pumps with suction-side volume flow control by means of a feed metering unit in combination with spring-loaded intake valves, which have the drawback that at a high pump speed, constant delivery cannot be guaranteed and that pressure fluctuations in the low pressure circuit can lead to noise, advantageously a cost reduction can be achieved by the omission of a feed metering unit, even at high pump speeds a constant delivery can be made possible and noise reduction can be achieved by the avoidance of pressure fluctuations and possible cavitation in the low pressure circuit.
- In a conventional design, in particular in multi-piston pumps with three or more pistons, the suction phases overlap. Pressure fluctuations then lead to particularly great differences in the quantity delivered. This can advantageously be avoided. Here it is possible to exclude such differences in the pre-stored quantity.
- In particular a great cost advantage is achieved with a high-pressure pump designed as a single piston pump. Even when designed as a two-piston pump with a further actuator, the absence of bores in the housing of the high-pressure pump partially compensates for extra costs. One essential advantage of direct control is the expansion of the pump rotation speed range and hence an improvement in the efficiency of the high-pressure pump.
- Also integration of the inlet valve into the cylinder head allows a very small construction size. This also applies for very high pressures, for example of 300 MPa (3000 bar) as conceivable for application on trucks.
- Advantageously the inlet valve is formed as a magnetically controllable inlet valve. Furthermore it is advantageous that the inlet valve is fixed to the cylinder head by means of a screw plug screwed into the cylinder head, and that the screw plug is formed of a ferromagnetic material. As a result the screw plug can serve as a magnetic conductor which improves the efficiency of the magnetic circuit and allows a high magnetic force.
- Also it is advantageous for a magnet coil to be provided, that the inlet valve can be controlled via current flowing through the magnet coil, and that the magnet coil can be cooled by fuel that can be transferred via the inlet valve to the pump working chamber. Thus cooling of the magnet coil and further elements of the magnetic circuit can be achieved by flushing with the fuel.
- It is also advantageous that the inlet valve has a valve body and a valve tappet co-operating with the valve body to form a seal seat, wherein the valve tappet lies on the cylinder head, wherein a magnetically activatable solenoid plunger is provided and wherein the solenoid plunger carries the valve tappet with it on mechanical activation to open the seal seat formed between the valve body and the valve tappet. Thereby the magnetic force to activate the inlet valve can be generated via the solenoid plunger, wherein the screw plug advantageously serves as a magnetic conductor. The inlet valve is here preferably closed when the magnet coil is switched without current. If current flows through the magnet coil of the magnet and the pump piston is for example at the top dead center, then the inlet valve opens. On full filling, the inlet valve is preferably open until the bottom dead center of the pump piston. It is furthermore advantageous here that an adjustment shim is provided which serves to specify a working air gap and a residual air gap for the solenoid plunger. This allows a modular design wherein by fitting of a suitable adjustment shim, adaptation is possible to the respective application of the high-pressure pump. This expands the application range of the high-pressure pump, wherein simple adaptation and largely identical design of the high-pressure pump are possible.
- It is also advantageous that a controller is provided which controls the inlet valve as a function of movement of the pump piston of the pump assembly. Firstly it is advantageous that the controller, to reduce the filling of the pump working chamber of the pump assembly, shortens the control time at its end so that the inlet valve is closed before the pump piston reaches the bottom dead center, or extends the control time at its end so that the inlet valve is closed after the pump piston reaches a bottom dead center. Thus the control time can be reduced so that the inlet valve is closed again before the pump piston reaches the bottom dead center, which reduces the quantity of fuel flowing into the pump working chamber. This can alternatively also be achieved in that the injector valve is only closed after the reaching of the bottom dead center, whereby the fuel transferred to the pump working chamber is returned partly via the inlet valve in the opposite direction by the movement of the pump piston. In the first case the pressure fluctuations on the low pressure side are reduced. In the second case preferably no cavities occur in the working cylinder. The advantageous variant may be selected specially depending on the application. A further possibility is that the control time is shortened at its start so that the inlet valve is opened only after the pump piston reaches a top dead center. Thus the inlet valve is not opened immediately after the top dead center, so that the quantity of fuel flowing into the pump working chamber is also reduced. Here also a suitable combination of control methods can be performed by the controller. For example the control time can be shortened both at its start and at its end. Thus advantageously partial fillings of the pump working chamber can be achieved. Furthermore pressure fluctuations can be influenced positively with regard to amplitude and frequency by one or more chokes connected before the inlet valve. Also the quantity regulation can be positively influenced. In this way the noise behavior, which can be unfavorably affected by pressure fluctuations in the low pressure, can be improved.
- The inlet valve is preferably fitted with a closing spring with a high spring pretension to achieve a high closing dynamic.
- Preferred embodiment examples of the invention are described in more detail in the description below with reference to the enclosed drawing. This shows:
-
FIG. 1 a high-pressure pump in an extract, schematic, axial cross section view corresponding to one embodiment example of the invention. -
FIG. 1 shows a high-pressure pump 1 in an extract, schematic, axial cross section view corresponding to one embodiment example of the invention. The high-pressure pump 1 can in particular be designed as a radial or in-line piston pump. The high-pressure pump 1 is particularly suitable as a fuel pump for fuel injection systems of air-compressing, auto-ignition internal combustion engines. A preferred use of the high-pressure pump 1 lies in a fuel injection system with a fuel distribution rail which stores diesel fuel under high pressure. The high-pressure pump 1 according to the invention is however also suitable for other applications. In particular the high-pressure pump can be used as a piston pump to deliver suitable fluids, in particular fluids other than fuel. - The high-pressure pump 1 has a pump housing which is mounted on a
cylinder head 2. Thecylinder head 2 has a shoulder 3 which protrudes into a bore in the pump housing. Here in the shoulder 3 is formed a cylinder bore 4 in which a pump piston 5 of a pump assembly 6 is guided along anaxis 7. - The high-pressure pump 1 also has a
drive shaft 8 on which is provided a cam 9. The cam 9 can here also be designed as a multiple cam or as an eccentric segment of thedrive shaft 8. In operation thedrive shaft 8 with the cam 9 rotates about arotary axis 10. Between the pump piston 5 of the pump assembly 6 and the cam 9 is anactive connection 11 which is illustrated by thedouble arrow 11. For example via a roller shoe and a roller mounted in the roller shoe, an actuation force can be transferred by the cam 9 to the pump piston 5. A return of the pump piston 5 can take place via a suitable tappet spring. - Thus the pump assembly 6 can be driven by the cam 9 of the
drive shaft 8. Depending on the design of the high-pressure pump 1, further pump assemblies can also be driven by the cam 9. Also on thedrive shaft 8 can be provided further cams which serve to drive further pump assemblies. Depending on the design, a high-pressure pump 1 can thus be constructed as a radial or in-line piston pump. - The pump piston 5 in the cylinder bore 4 delimits a
pump working chamber 12. Asupply channel 13 serves to supply fuel which is delivered therein by a pre-delivery pump. In thesupply channel 13 are provided afirst choke 14 and asecond choke 15. Thesupply channel 13 leads into alow pressure chamber 16 which is formed by arecess 17 in thecylinder head 2. - The high-pressure pump 1 has an
inlet valve 20. Thelow pressure chamber 16 is here part of theinlet valve 20. Theinlet valve 20 is integrated in thecylinder head 2. Theinlet valve 20 is arranged in therecess 17 of thecylinder head 2. Therecess 17 is here closed by ascrew plug 21. Thus thelow pressure chamber 16 is closed to the environment. The screw plug 21 acts via avalve part 22 on avalve body 23. The screw plug 21 is screwed into thecylinder head 2 and through this presses thevalve body 23 against acontact surface 24 formed on thecylinder head 2. Thescrew plug 21,valve part 22 andvalve body 23 of theinlet valve 20 are thus fixed in a stationary manner. Also thescrew plug 21 andvalve part 22 are preferably formed of ferromagnetic material. - In the
valve body 23 is guided avalve tappet 25. Here thevalve tappet 25 co-operates with avalve seat surface 26 formed on thevalve body 23 to form a seal seat. Avalve spring 27 presses thevalve tappet 25 against thevalve seat surface 26. Thevalve spring 27 here acts via avalve element 28 and anadjustment shim 29 on arotor 30. Therotor 30 is formed as asolenoid plunger 30. Thesolenoid plunger 30 is connected with thevalve tappet 25. Thus thevalve tappet 25 is pressurized by the pretension of thevalve spring 27. Thevalve tappet 25,valve element 28,adjustment shim 29 andsolenoid plunger 30 of theinlet valve 20 are mobile elements which are moved to open theinlet valve 20 on control of theinlet valve 20. - The
inlet valve 20 also has amagnet 31 with amagnet coil 32. Themagnet coil 32 is electrically connected via electrically conductive contact pins 33, 34 withpins plug 37. Theplug 37 here allows connection with acontrol unit 38. Thecontrol unit 38 in this embodiment example serves as acontroller 38. Thecontroller 38 can also be integrated in a central control unit. Thecontrol unit 38 is connected with arotary angle sensor 39 which detects the momentary rotation angle of thedrive shaft 8 and emits this to thecontrol unit 38. Via the rotary angle detected, there is a direct connection to the momentary position of the pump piston 5. It can in particular be detected thus whether the pump piston 5 is at a top dead center at which the pump piston undergoes a maximum stroke and thepump working chamber 12 has minimum volume. Accordingly it can be detected whether the pump piston 5 is at a bottom dead center at which the pump piston 5 has minimum stroke and the volume of thepump working chamber 12 is maximum. - Current flowing through the
magnet coil 32 generates a magnetic flux. This magnetic flux is emitted by themagnet 31 wherein an amplification is possible via theferromagnetic screw plug 21. The magnetic flux also runs via thevalve part 22, thesolenoid plunger 30 and where applicable further ferromagnetic elements back to thescrew plug 21. Between thesolenoid plunger 30 and thevalve part 22 there is agap 40. Thegap 40 firstly allows displaceability of thesolenoid plunger 30 and thus an adjustment of thevalve tappet 25 to activate theinlet valve 20. Secondly at least one rest air gap remains asgap 40 in order to avoid, in activated state, a so-called magnetic adhesion effect of thesolenoid plunger 30 on thevalve part 22. In particular when the power to themagnet coil 32 is switched off, the force of thevalve spring 27 can initiate a closure of theinlet valve 20 largely without distortion. The maximum size of thegap 40 is specified by the sum of the desired working air gap and the residual air gap. Adjustment of the residual air gap and working air gap is possible by suitable selection ofvalve element 28 andadjustment shim 29. In particular the thickness of theadjustment shim 29 can pre-specify the desired working air gap. The thickness of theadjustment shim 29 thus specifies the stroke of thevalve tappet 25. With unchanged geometry in the region of thevalve seat surface 26, thus the opening cross section at thevalve seat surface 26 can be changed and hence also the possible throughflow into thepump working chamber 12 set when the seal seat is opened. Thus theinlet valve 20 can be adapted in relation to the application concerned. - By actuating
inlet valve 20, fuel can thus be guided from the low-pressure chamber 16 to thepump working chamber 12. Activation of theinlet valve 20 here takes place during a suction stroke of the pump piston 5. During the delivery stroke of the pump piston 5, theinlet valve 20 is preferably closed. Thus fuel under high pressure is delivered via outlet valve 41—which can be designed as a directional or non-return valve 41—into a high-pressure line 42. The high-pressure line 42 is for example connected with a fuel distribution rail. - If the
inlet valve 20 is opened at approximately the top dead center of a pump piston 5 and closed at the bottom dead center of pump piston 5, a full filling of thepump working chamber 12 can be achieved. However theinlet valve 20 can be controlled by thecontroller 38 irrespective of the stroke or momentary position of pump piston 5 during the suction phase. This allows also a partial filling of thepump working chamber 12. There are several possibilities for this which can be combined where applicable. - One possibility is to reduce the control time of the
inlet valve 20 so that theinlet valve 20 is closed again before the pump piston 5 reaches the bottom dead center. Alternatively the control time can also be extended beyond the reaching of the bottom dead center. Theinlet valve 20 is thus only closed after pump piston 5 reaches the bottom dead center so that part of the fuel is delivered back from thepump working chamber 12 during the stroke of the pump piston 5 in the direction back through theinlet valve 20. The other part of the fuel is delivered then via the high-pressure line 42. The quantity of fuel delivered via the high-pressure line 42 per pump stroke is thus reduced. - It should be noted that there is no shut-off control of fuel to a tank or similar. Also in this way where applicable noise behavior can be improved by damping pressure pulses. Adjustment is possible via
chokes - A further possibility of achieving a partial filling is that the inlet valve is not opened immediately after pump piston 5 reaches the top dead center. This achieves a certain idle stroke of the pump piston 5 so that the entirety of fuel flowing into the
pump working chamber 12 via the opening cross section of the opened seat seal is thus reduced. - Thus advantageously through one or
more chokes inlet valve 20 or where applicable several inlet valves designed corresponding to theinlet valve 20, pressure and attenuation waves occur which run from the intake valves to a delivery pump, in particular an electric fuel pump, and are reflected there. The reflected waves can inter alia make contact again on an opening process of theinlet valve 20 and thus further influence the filled mass in the pump working chamber, which can lead to delivery fluctuations of the high-pressure pump. By use of damping volumes and chokes 14, 15 in thesupply channel 13 and by matching these, such pressure waves can be reduced so far that a constant delivery of the high-pressure pump 1 is guaranteed within a certain tolerance range. The design and dimensioning here depend on the area of application of the high-pressure pump 1 and the connection to the pre-delivery pump. - Advantageously thus an
intake valve 20 can be produced which is closed in the unpowered state. Thisinlet valve 20 is integrated in thecylinder head 2. The solenoid plunger principle can be utilized here so that rapid opening and closing of theintake valve 20 can be achieved. Furthermore the suction choking can be shifted into the working cylinder with deliberate utilization of an air exhalation. The necessary dynamic can be guaranteed by one or more connecting bores. A sufficiently high closing dynamic can be achieved via a correspondingly high spring pretension ofvalve spring 27. The cooling of themagnet 31 with themagnet coil 32 can be achieved by flushing with fuel. - The invention is not restricted to the embodiment examples described.
Claims (11)
1. A high-pressure pump (1) for fuel injection systems of air-compressing, auto-ignition internal combustion engines, with at least one cylinder head (2) and a pump assembly (6), wherein the cylinder head (2) has a cylinder bore (4) in which is guided a pump piston (5) of the pump assembly (6), wherein the pump piston (5) in the cylinder bore (4) delimits a pump working chamber (12), wherein an inlet valve (20) integrated in the cylinder head (2) is provided via which fuel can be transferred to the pump working chamber (12) and whereby, by control of the inlet valve (20), a metered feed of the fuel guided into the pump working chamber (12) is possible.
2. The high-pressure pump as claimed in claim 1 , characterized in that the inlet valve (20) is formed as a magnetically controllable inlet valve (20).
3. The high-pressure pump as claimed in claim 2 , characterized in that the inlet valve (20) is fixed to the cylinder head (2) by means of a screw plug (21) screwed into the cylinder head (2) and that the screw plug (21) is made of a ferromagnetic material.
4. The high-pressure pump as claimed in claim 1 , characterized in that a magnet coil (32) is provided, that current flowing through the magnet coil (32) allows control of the inlet valve (20), and that the magnet coil (32) can be cooled by fuel which can be transferred via the inlet valve (20) to the pump working chamber (12).
5. The high-pressure pump as claimed in claim 1 , characterized in that the inlet valve (20) comprises a valve body (23) and a valve tappet (25) co-operating with the valve body (23) to form a seal seat, wherein the valve tappet (25) lies against the cylinder head (2), wherein a magnetically activatable solenoid plunger (30) is provided and wherein the solenoid plunger (30) carries the valve tappet (25) with it on magnetic actuation to open the seal seat formed between the valve body (23) and the valve tappet (25).
6. The high-pressure pump as claimed in claim 5 , characterized in that an adjustment shim (29) is provided which serves to specify a working air gap for the solenoid plunger (30).
7. The high-pressure pump as claimed in claim 1 , characterized in that a controller (38) is provided which controls the inlet valve (20) as a function of movement of the pump piston (5) of the pump assembly (6).
8. The high-pressure pump as claimed in claim 7 , characterized in that to reduce a filling of the pump working chamber (12) of the pump assembly (6), the controller (38) at least one of:
a) shortens the control time at its end so that the inlet valve (20) is closed before the pump piston (5) reaches a bottom dead center, or
extends the control time at its end so that the inlet valve (20) is closed after the pump piston (5) reaches a bottom dead center, and
b) shortens the control time at its start so that the inlet valve (20) is opened after the pump piston (5) reaches a top dead center.
9. The high-pressure pump as claimed in claim 1 , characterized in that the inlet valve (20) has a low pressure chamber (16) which is formed in a recess (17) of the cylinder head (2) in which the inlet valve (20) is arranged and in that at least one of the low pressure chamber (16) is closed by a screw plug (21) of the inlet valve (20), and that a supply channel (13) leading to the low pressure chamber (16) is provided and that in the supply channel (13) is arranged at least one of at least one choke (14, 15) and at least one damping volume.
10. The high-pressure pump as claimed in claim 1 , characterized in that the inlet valve (20) has a closing spring (27) and that the closing spring (27) has a high spring pretension.
11. The high-pressure pump as claimed in claim 1 , characterized in that the high-pressure pump is one of a radial and an in-line piston pump.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010027745A DE102010027745A1 (en) | 2010-04-14 | 2010-04-14 | high pressure pump |
DE102010027745.2 | 2010-04-14 | ||
PCT/EP2011/053101 WO2011128150A1 (en) | 2010-04-14 | 2011-03-02 | High-pressure pump |
Publications (1)
Publication Number | Publication Date |
---|---|
US20130022484A1 true US20130022484A1 (en) | 2013-01-24 |
Family
ID=43924861
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/579,190 Abandoned US20130022484A1 (en) | 2010-04-14 | 2011-03-02 | High-pressure pump |
Country Status (8)
Country | Link |
---|---|
US (1) | US20130022484A1 (en) |
EP (1) | EP2558708A1 (en) |
JP (1) | JP5886830B2 (en) |
KR (1) | KR20130056858A (en) |
CN (1) | CN102859178B (en) |
DE (1) | DE102010027745A1 (en) |
RU (1) | RU2559095C2 (en) |
WO (1) | WO2011128150A1 (en) |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2770202A1 (en) * | 2013-02-22 | 2014-08-27 | Mitsubishi Heavy Industries, Ltd. | Control valve, assembly method of control valve, and power generating apparatus of renewable energy type |
JP2015525847A (en) * | 2012-07-19 | 2015-09-07 | デルファイ・インターナショナル・オペレーションズ・ルクセンブルク・エス・アー・エール・エル | Valve assembly |
US20150316012A1 (en) * | 2012-12-18 | 2015-11-05 | Delphi International Operations Luxembourg S.A.R. L. | Pump unit |
US20160108875A1 (en) * | 2013-05-29 | 2016-04-21 | Robert Bosch Gmbh | High pressure pump for a fuel injection system |
US20170248309A1 (en) * | 2013-01-17 | 2017-08-31 | Pond Technologies Inc. | Process for managing photobioreactor exhaust |
WO2017213984A1 (en) * | 2016-06-06 | 2017-12-14 | Stanadyne Llc | Partial charging of single piston fuel pump |
US20180187638A1 (en) * | 2015-07-02 | 2018-07-05 | Robert Bosch Gmbh | Electromagnetically actuable intake valve for a high-pressure pump, and high-pressure pump |
US10801456B2 (en) | 2015-10-27 | 2020-10-13 | Delphi Technologies Ip Limited | Control valve arrangement of a fuel injector |
US11346331B2 (en) | 2016-09-26 | 2022-05-31 | Vitesco Technologies GmbH | High-pressure pump in a high-pressure injection system of a vehicle |
US11421637B2 (en) | 2015-01-05 | 2022-08-23 | Cummins Inc. | High pressure diesel fuel pump pumping element |
US11668261B2 (en) | 2019-04-22 | 2023-06-06 | Cummins Inc. | Pump active inlet valve spilling residual pressure |
Families Citing this family (31)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012200455A1 (en) | 2012-01-13 | 2013-07-18 | Robert Bosch Gmbh | Inlet valve i.e. suction valve, for supplying fuel from low pressure system into operating chamber of fuel high pressure pump of internal combustion engine, has supply channel including inclination, which is aligned towards valve seat |
DE102012213546A1 (en) | 2012-08-01 | 2014-02-06 | Robert Bosch Gmbh | High pressure pump for internal combustion engines |
DE102012222442A1 (en) | 2012-12-06 | 2014-06-26 | Robert Bosch Gmbh | Suction valve for high pressure pump of fuel injection system, particularly common-rail injection system, has valve piston which is formed multipart and comprises two portions which are temporarily coupled or uncoupled by coupling unit |
JP2014224519A (en) * | 2013-05-17 | 2014-12-04 | ボッシュ株式会社 | Fuel press-feeding control method and common rail type fuel injection control device |
DE102013215909A1 (en) | 2013-08-12 | 2015-02-12 | Robert Bosch Gmbh | Method for controlling and regulating a high-pressure fuel pump of an internal combustion engine provided with an inlet valve with an electromagnetic actuator |
DE102013218854A1 (en) | 2013-09-19 | 2015-03-19 | Robert Bosch Gmbh | Electromagnetically controllable suction valve |
DE102013218844A1 (en) * | 2013-09-19 | 2015-03-19 | Robert Bosch Gmbh | Electromagnetically controllable suction valve |
DE102013220593A1 (en) | 2013-10-11 | 2015-04-16 | Robert Bosch Gmbh | Electromagnetically controllable suction valve |
DE102013225162A1 (en) * | 2013-12-06 | 2015-06-11 | Robert Bosch Gmbh | Electromagnetically actuated valve |
WO2015090446A1 (en) | 2013-12-20 | 2015-06-25 | Robert Bosch Gmbh | Inlet valve for a high-pressure pump and high-pressure pump |
CN104763569B (en) * | 2014-01-06 | 2018-05-11 | 联合汽车电子有限公司 | Using the high-pressure pump of copper brazing technology |
DE102014201101A1 (en) | 2014-01-22 | 2015-07-23 | Robert Bosch Gmbh | Electromagnetically controllable suction valve |
DE102014201789B4 (en) | 2014-01-31 | 2022-01-05 | Bayerische Motoren Werke Aktiengesellschaft | Drive system of a high-pressure fuel pump, high-pressure fuel pump assembly and combustion engine |
DE102014202334A1 (en) | 2014-02-10 | 2015-08-13 | Robert Bosch Gmbh | High pressure pump for a fuel injection system |
DE102014207937A1 (en) * | 2014-04-28 | 2015-10-29 | Robert Bosch Gmbh | Solenoid valve for a fuel injection system |
DE102014207941A1 (en) | 2014-04-28 | 2015-10-29 | Robert Bosch Gmbh | Electromagnetically controllable inlet valve for a high-pressure fuel pump |
US9874185B2 (en) * | 2014-05-21 | 2018-01-23 | Ford Global Technologies, Llc | Direct injection pump control for low fuel pumping volumes |
DE102014214231A1 (en) | 2014-07-22 | 2016-01-28 | Robert Bosch Gmbh | Electromagnetic actuator for a suction valve and suction valve |
DE102014220975A1 (en) | 2014-10-16 | 2016-04-21 | Robert Bosch Gmbh | Electromagnetically actuated inlet valve and high-pressure pump with inlet valve |
DE102014221674A1 (en) * | 2014-10-24 | 2016-04-28 | Robert Bosch Gmbh | Method for controlling an electrically controllable suction valve |
DE102014225191A1 (en) | 2014-12-09 | 2016-06-09 | Robert Bosch Gmbh | Suction valve for a high pressure pump of a fuel injection system |
DE102015007465A1 (en) * | 2015-06-09 | 2016-12-15 | Thomas Magnete Gmbh | Reciprocating pump with inlet-side flow limitation and method for operating the reciprocating pump |
DE102015218054A1 (en) | 2015-09-21 | 2017-03-23 | Robert Bosch Gmbh | Valve, in particular suction valve, in a high-pressure pump of a fuel injection system |
DE102016107966A1 (en) * | 2016-04-06 | 2017-10-12 | Volkswagen Aktiengesellschaft | Demand-oriented high-pressure pump with variable speed |
DE102016216343A1 (en) | 2016-08-30 | 2018-03-01 | Robert Bosch Gmbh | Method for controlling an electromagnetically controllable inlet valve |
JP6525016B2 (en) | 2017-01-12 | 2019-06-05 | トヨタ自動車株式会社 | Control device for internal combustion engine |
DE102018206334A1 (en) * | 2018-04-25 | 2019-10-31 | Robert Bosch Gmbh | Fuel delivery device for cryogenic fuels |
DE102018212665A1 (en) * | 2018-07-30 | 2020-01-30 | Robert Bosch Gmbh | Piston pump and fuel delivery device for cryogenic fuels |
DE102019116353B4 (en) * | 2019-06-17 | 2020-12-24 | Man Energy Solutions Se | Fuel pump |
CN110761993B (en) * | 2019-11-25 | 2021-08-20 | 宁波捷尔天电气有限公司 | Plug-type antiseized even plunger electromagnetic pump |
DE102021004283A1 (en) | 2021-08-21 | 2023-02-23 | Kastriot Merlaku | high pressure pump |
Citations (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4385614A (en) * | 1979-04-06 | 1983-05-31 | Robert Bosch Gmbh | Fuel injection pump for internal combustion engines |
US4526150A (en) * | 1983-03-05 | 1985-07-02 | Robert Bosch Gmbh | Fuel injection apparatus for internal combustion engines |
US4838233A (en) * | 1986-03-05 | 1989-06-13 | Nippondenso Co., Ltd. | Pilot injection system for fuel injection pump |
US5150688A (en) * | 1989-10-20 | 1992-09-29 | Robert Bosch Gmbh | Magnet valve, in particular for fuel injection pumps |
US5911208A (en) * | 1996-11-25 | 1999-06-15 | Toyota Jidosha Kabushiki Kaisha | High-pressure fuel supply device for internal combustion engine |
US5957674A (en) * | 1996-07-01 | 1999-09-28 | Mitsubishi Denki Kabushiki Kaisha | Variable-discharge high pressure pump |
US6016790A (en) * | 1996-07-05 | 2000-01-25 | Nippon Soken, Inc. | High-pressure pump for use in fuel injection system for diesel engine |
US6345608B1 (en) * | 1998-07-29 | 2002-02-12 | Robert Bosch Gmbh | Fuel supply system for an internal combustion engine |
US6447273B1 (en) * | 1998-12-24 | 2002-09-10 | Isuzu Motors Limited | Variable-delivery high-pressure fuel pump |
US6470857B2 (en) * | 2000-06-26 | 2002-10-29 | Denso Corporation | Flow amount control device |
US6530363B1 (en) * | 1999-04-16 | 2003-03-11 | Caterpillar Inc | Variable delivery pump and common rail fuel system using the same |
US6546917B2 (en) * | 2000-10-05 | 2003-04-15 | Mitsubishi Denki Kabushiki Kaisha | Variable delivery fuel supply device |
US6554590B2 (en) * | 2000-04-18 | 2003-04-29 | Toyota Jidosha Kabushiki Kaisha | High pressure pump |
US7198033B2 (en) * | 2004-03-26 | 2007-04-03 | Denso Corporation | Fuel supply system of internal combustion engine |
US20090104045A1 (en) * | 2005-01-19 | 2009-04-23 | Denso Corporation | High pressure pump having plunger |
US7552720B2 (en) * | 2007-11-20 | 2009-06-30 | Hitachi, Ltd | Fuel pump control for a direct injection internal combustion engine |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3077738B2 (en) | 1994-04-28 | 2000-08-14 | 株式会社デンソー | High pressure supply pump |
DE19717493A1 (en) * | 1997-04-25 | 1998-10-29 | Bosch Gmbh Robert | Fuel injection system |
JPH11336637A (en) * | 1998-05-25 | 1999-12-07 | Nippon Soken Inc | Variable discharge amount high pressure pump |
JP4088738B2 (en) * | 1998-12-25 | 2008-05-21 | 株式会社デンソー | Fuel injection pump |
JP3721860B2 (en) * | 1999-06-18 | 2005-11-30 | いすゞ自動車株式会社 | Fuel supply pump |
JP2002266728A (en) * | 2001-03-13 | 2002-09-18 | Denso Corp | Fuel control valve and high pressure fuel pump |
DE10134066A1 (en) * | 2001-07-13 | 2003-02-06 | Bosch Gmbh Robert | Fuel pump, in particular high-pressure fuel pump for a fuel system of an internal combustion engine with gasoline direct injection |
JP4042058B2 (en) * | 2003-11-17 | 2008-02-06 | 株式会社デンソー | Fuel injection device for internal combustion engine |
DE102004013244A1 (en) * | 2004-03-18 | 2005-10-06 | Robert Bosch Gmbh | High-pressure pump, in particular for a fuel injection device of an internal combustion engine |
JP4552694B2 (en) * | 2005-03-02 | 2010-09-29 | トヨタ自動車株式会社 | Vehicle fuel supply device |
CN100473821C (en) * | 2005-03-30 | 2009-04-01 | 株式会社电装 | Fuel pump having plunger and fuel supply system using the same |
JP2007120492A (en) * | 2005-09-29 | 2007-05-17 | Denso Corp | High pressure fuel pump |
DE102008040083A1 (en) * | 2008-07-02 | 2010-01-07 | Robert Bosch Gmbh | high pressure pump |
-
2010
- 2010-04-14 DE DE102010027745A patent/DE102010027745A1/en not_active Withdrawn
-
2011
- 2011-03-02 JP JP2013504182A patent/JP5886830B2/en not_active Expired - Fee Related
- 2011-03-02 CN CN201180018667.9A patent/CN102859178B/en not_active Expired - Fee Related
- 2011-03-02 US US13/579,190 patent/US20130022484A1/en not_active Abandoned
- 2011-03-02 EP EP11709035A patent/EP2558708A1/en not_active Withdrawn
- 2011-03-02 WO PCT/EP2011/053101 patent/WO2011128150A1/en active Application Filing
- 2011-03-02 RU RU2012148170/06A patent/RU2559095C2/en not_active IP Right Cessation
- 2011-03-02 KR KR1020127026733A patent/KR20130056858A/en not_active Application Discontinuation
Patent Citations (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4385614A (en) * | 1979-04-06 | 1983-05-31 | Robert Bosch Gmbh | Fuel injection pump for internal combustion engines |
US4526150A (en) * | 1983-03-05 | 1985-07-02 | Robert Bosch Gmbh | Fuel injection apparatus for internal combustion engines |
US4838233A (en) * | 1986-03-05 | 1989-06-13 | Nippondenso Co., Ltd. | Pilot injection system for fuel injection pump |
US5150688A (en) * | 1989-10-20 | 1992-09-29 | Robert Bosch Gmbh | Magnet valve, in particular for fuel injection pumps |
US5957674A (en) * | 1996-07-01 | 1999-09-28 | Mitsubishi Denki Kabushiki Kaisha | Variable-discharge high pressure pump |
US6016790A (en) * | 1996-07-05 | 2000-01-25 | Nippon Soken, Inc. | High-pressure pump for use in fuel injection system for diesel engine |
US5911208A (en) * | 1996-11-25 | 1999-06-15 | Toyota Jidosha Kabushiki Kaisha | High-pressure fuel supply device for internal combustion engine |
US6345608B1 (en) * | 1998-07-29 | 2002-02-12 | Robert Bosch Gmbh | Fuel supply system for an internal combustion engine |
US6447273B1 (en) * | 1998-12-24 | 2002-09-10 | Isuzu Motors Limited | Variable-delivery high-pressure fuel pump |
US6530363B1 (en) * | 1999-04-16 | 2003-03-11 | Caterpillar Inc | Variable delivery pump and common rail fuel system using the same |
US6554590B2 (en) * | 2000-04-18 | 2003-04-29 | Toyota Jidosha Kabushiki Kaisha | High pressure pump |
US6470857B2 (en) * | 2000-06-26 | 2002-10-29 | Denso Corporation | Flow amount control device |
US6546917B2 (en) * | 2000-10-05 | 2003-04-15 | Mitsubishi Denki Kabushiki Kaisha | Variable delivery fuel supply device |
US7198033B2 (en) * | 2004-03-26 | 2007-04-03 | Denso Corporation | Fuel supply system of internal combustion engine |
US20090104045A1 (en) * | 2005-01-19 | 2009-04-23 | Denso Corporation | High pressure pump having plunger |
US7604462B2 (en) * | 2005-01-19 | 2009-10-20 | Denso Corporation | High pressure pump having plunger |
US7552720B2 (en) * | 2007-11-20 | 2009-06-30 | Hitachi, Ltd | Fuel pump control for a direct injection internal combustion engine |
Cited By (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9970399B2 (en) | 2012-07-19 | 2018-05-15 | Delphi Technologies Ip Limited | Valve assembly |
JP2015525847A (en) * | 2012-07-19 | 2015-09-07 | デルファイ・インターナショナル・オペレーションズ・ルクセンブルク・エス・アー・エール・エル | Valve assembly |
US20150316012A1 (en) * | 2012-12-18 | 2015-11-05 | Delphi International Operations Luxembourg S.A.R. L. | Pump unit |
US20170248309A1 (en) * | 2013-01-17 | 2017-08-31 | Pond Technologies Inc. | Process for managing photobioreactor exhaust |
EP2770202A1 (en) * | 2013-02-22 | 2014-08-27 | Mitsubishi Heavy Industries, Ltd. | Control valve, assembly method of control valve, and power generating apparatus of renewable energy type |
US10100795B2 (en) * | 2013-05-29 | 2018-10-16 | Robert Bosch Gmbh | High pressure pump for a fuel injection system |
US20160108875A1 (en) * | 2013-05-29 | 2016-04-21 | Robert Bosch Gmbh | High pressure pump for a fuel injection system |
US11421637B2 (en) | 2015-01-05 | 2022-08-23 | Cummins Inc. | High pressure diesel fuel pump pumping element |
US20180187638A1 (en) * | 2015-07-02 | 2018-07-05 | Robert Bosch Gmbh | Electromagnetically actuable intake valve for a high-pressure pump, and high-pressure pump |
US10400728B2 (en) * | 2015-07-02 | 2019-09-03 | Robert Bosch Gmbh | Electromagnetically actuable intake valve for a high-pressure pump, and high-pressure pump |
US10801456B2 (en) | 2015-10-27 | 2020-10-13 | Delphi Technologies Ip Limited | Control valve arrangement of a fuel injector |
WO2017213984A1 (en) * | 2016-06-06 | 2017-12-14 | Stanadyne Llc | Partial charging of single piston fuel pump |
CN109312703A (en) * | 2016-06-06 | 2019-02-05 | 斯坦蒂内有限责任公司 | It loads the part of single-piston petrolift |
EP3464872A4 (en) * | 2016-06-06 | 2020-01-08 | Stanadyne LLC | Partial charging of single piston fuel pump |
US11346331B2 (en) | 2016-09-26 | 2022-05-31 | Vitesco Technologies GmbH | High-pressure pump in a high-pressure injection system of a vehicle |
US11668261B2 (en) | 2019-04-22 | 2023-06-06 | Cummins Inc. | Pump active inlet valve spilling residual pressure |
Also Published As
Publication number | Publication date |
---|---|
RU2012148170A (en) | 2014-06-10 |
DE102010027745A1 (en) | 2011-10-20 |
JP2013527365A (en) | 2013-06-27 |
KR20130056858A (en) | 2013-05-30 |
CN102859178B (en) | 2016-01-20 |
RU2559095C2 (en) | 2015-08-10 |
CN102859178A (en) | 2013-01-02 |
EP2558708A1 (en) | 2013-02-20 |
JP5886830B2 (en) | 2016-03-16 |
WO2011128150A1 (en) | 2011-10-20 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20130022484A1 (en) | High-pressure pump | |
US8882475B2 (en) | Electromagnetic flow rate control valve and high-pressure fuel supply pump using the same | |
CN105804907B (en) | High-pressure fuel supply pump with electromagnetic suction valve | |
US20100206252A1 (en) | High-pressure pump for a fuel system of an internal combustion engine | |
US8911218B2 (en) | Fuel pump | |
JP4681119B2 (en) | Radial piston pump for high pressure fuel generation | |
JPH10141177A (en) | High pressure pump | |
US20060159573A1 (en) | High pressure pump having downsized structure | |
US11098710B2 (en) | Inlet control valve for high pressure fuel pump | |
US20090199820A1 (en) | Pressure control valve with limp-home and ventilation function | |
US6651625B1 (en) | Fuel system and pump suitable for use therein | |
US6237573B1 (en) | Variable delivery fuel supply device | |
US9435328B2 (en) | Variable stroke control structure for high pressure fuel pump | |
JP2002115623A (en) | Variable discharge-amount fuel supply device | |
JP2003314409A (en) | Fuel injection system for internal combustion engine | |
US8464692B2 (en) | Device for supplying an internal combustion engine with fuel | |
JP4787444B2 (en) | Radial piston pump | |
JP5316163B2 (en) | Flow control valve | |
JP2017145731A (en) | High pressure fuel supply pump | |
JP3693463B2 (en) | Variable discharge high pressure pump | |
WO2000055495A1 (en) | Fuel feed pump | |
EP2256334B1 (en) | A fuel-supply system for an internal-combustion engine | |
JP4640387B2 (en) | High pressure pump and fuel supply device for internal combustion engine | |
CN113994090A (en) | Pump, in particular high-pressure fuel pump | |
KR20010019594A (en) | High pressure supply for fuel injection device |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: ROBERT BOSCH GMBH, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:FUCHS, WALTER;RODRIGUEZ-AMAYA, NESTOR;BOEHLAND, PETER;AND OTHERS;SIGNING DATES FROM 20120615 TO 20120702;REEL/FRAME:028793/0136 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |