CN104870801B - High-pressure injection system - Google Patents
High-pressure injection system Download PDFInfo
- Publication number
- CN104870801B CN104870801B CN201380065742.6A CN201380065742A CN104870801B CN 104870801 B CN104870801 B CN 104870801B CN 201380065742 A CN201380065742 A CN 201380065742A CN 104870801 B CN104870801 B CN 104870801B
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- Prior art keywords
- valve
- check
- injector
- pressure
- return line
- Prior art date
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Links
- 238000002347 injection Methods 0.000 title claims description 55
- 239000007924 injection Substances 0.000 title claims description 55
- 239000000446 fuel Substances 0.000 claims abstract description 127
- 238000010992 reflux Methods 0.000 claims abstract description 15
- 230000010355 oscillation Effects 0.000 claims abstract description 12
- 238000002485 combustion reaction Methods 0.000 claims description 29
- 239000002828 fuel tank Substances 0.000 claims description 13
- 230000001050 lubricating effect Effects 0.000 description 20
- 238000005096 rolling process Methods 0.000 description 9
- 239000012530 fluid Substances 0.000 description 7
- 230000004048 modification Effects 0.000 description 5
- 238000012986 modification Methods 0.000 description 5
- 239000003981 vehicle Substances 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 3
- 239000003502 gasoline Substances 0.000 description 3
- 230000005611 electricity Effects 0.000 description 2
- 230000002045 lasting effect Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000000644 propagated effect Effects 0.000 description 2
- 239000007921 spray Substances 0.000 description 2
- 239000013589 supplement Substances 0.000 description 2
- 239000004359 castor oil Substances 0.000 description 1
- 235000019438 castor oil Nutrition 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000009969 flowable effect Effects 0.000 description 1
- ZEMPKEQAKRGZGQ-XOQCFJPHSA-N glycerol triricinoleate Natural products CCCCCC[C@@H](O)CC=CCCCCCCCC(=O)OC[C@@H](COC(=O)CCCCCCCC=CC[C@@H](O)CCCCCC)OC(=O)CCCCCCCC=CC[C@H](O)CCCCCC ZEMPKEQAKRGZGQ-XOQCFJPHSA-N 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/002—Arrangement of leakage or drain conduits in or from injectors
-
- 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
- F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
- F02M55/025—Common rails
-
- 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
- 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
- F02M63/005—Pressure relief valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
- F02M63/023—Means for varying pressure in common rails
- F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
-
- 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
- F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
- F02M69/46—Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
- F02M69/54—Arrangement of fuel pressure regulators
-
- 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
-
- 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
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
- F02M37/0023—Valves in the fuel supply and return system
- F02M37/0029—Pressure regulator in the low pressure fuel system
-
- 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
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0047—Layout or arrangement of systems for feeding fuel
- F02M37/0052—Details on the fuel return circuit; Arrangement of pressure regulators
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Ejector system (42), including：At least one injector (44), there is at least one reflux opening (56) for hydraulic coupler (51)；The injector return line (57) being connected with the guiding of at least one reflux opening (56) hydraulic pressure；First check-valve (58) in injector return line (57), first check-valve (58) is switched on fuel flowing direction in injector return line (57) away from least one injector (44), installed in injector return line (57) equipped with second check-valve (59) and second check-valve (59) relative to first check-valve (58) hydraulic parallel, second check-valve (59) is on fuel flowing direction towards being switched at least one injector (44) in injector return line (57), so as to which the pressure on fuel flowing direction in the injector return line (57) before first check-valve (58) can be improved in the pressure oscillation after first check-valve (58) using on fuel flowing direction.
Description
Technical field
The present invention relates to a kind of ejector system and a kind of high-pressure injection system.
Background technology
In the high-pressure injection system for internal combustion engine, especially in the common-rail injection system of diesel engine or gasoline engine,
High-pressure pump is continuously for the pressure in the high-pressure storage for maintaining common-rail injection system.High-pressure pump can be for example by internal combustion engine
Camshaft is driven by means of drive shaft.Pre- delivery pump such as gear pump or vane type drum pump are used to deliver the fuels to high pressure
Pump, the pre- delivery pump and high pressure series connection of pumps.Pre- delivery pump fuel is delivered to high-pressure pump from fuel tank by fuel conduit.
Piston pump is especially used as high-pressure pump.Drive shaft is supported by the housing.Piston is relative to the driving Axial and radial
Ground is arranged in the cylinder.Roller with roller-rolling surface is lain in the drive shaft with least one cam, the roller
It is supported in roller boots.Roller boots are connected with piston, so as to force piston to make to carry out reciprocal translational motion.Spring is in roller boots
The upper power applied radially toward drive shaft, so as to which roller is in lasting contact with drive shaft.Roller is with roller-rolling
Face is on axle-rolling surface as surface of the drive shaft with least one cam with drive shaft in contacting.Roller is borrowed
Help sliding supported condition in roller boots.
Here, drive shaft, roller and roller boots with least one cam are arranged within the lubricating chamber of high-pressure pump.From
The fuel that pre- delivery pump is delivered to high-pressure pump is guided by the lubricating chamber, so as on the one hand lubricate part within lubricating chamber and
The part is cooled down by the fuel guided by lubricating chamber.Therefore, the fuel of high-pressure pump is delivered in volume flow from pre- delivery pump
Include the on the one hand fuel of the part of high-pressure pump for being used to lubricate and be cooled within lubricating chamber by lubricating chamber's guiding and
Including the fuel for being used to be delivered to the determination of high voltage rail under high pressure for high-pressure pump.
The fuel conveyed by high-pressure pump is transported to high voltage rail and supplies electromagnetic injection valve from high voltage rail by pressure duct
Device.Fuel is ejected into the combustion chamber of internal combustion engine by electromagnetic injection valve device.Electromagnetic injection valve utensil has electromagnet as actuator.
Here, fuel is supplied into combustion chamber, the high-voltage tube under high pressure from jet chamber by means of the injector valve of electromagnetic injection valve device
Road is led in the jet chamber.Therefore, when opening injector valve by means of injector nozzle needle-valve, the fuel of jet chamber is in electricity
It is injected on magnet valve injector in combustion chamber.Here, injector nozzle needle-valve is hydraulically controlled by means of hydraulic coupler
Valve manipulates, that is, opens and closes.Therefore, the control valve of manipulation, i.e. opening and closing electromagnet, so as to the feelings closed in control valve
Leading and pressure decline of the fuel in control room in the case of control valve opening is accounted in control room mesohigh under condition, because
In the case where control valve is opened, fuel is discharged by injector return line from control room, because control valve opens and closes injection
Device return line.Here, injector return line is led in the fuel return line of high-pressure pump by check-valves.It is outstanding in high-pressure pump
In the case that it has the construction of only one piston, in fuel return line due to piston stroke motion and therefore lubricating
Caused stereomutation in room and there is strong pressure oscillation and flowed fluctuation.Check-valves tool in injector return line
There is task of the substantial constant pressure for example between 1 and 1.5bar is kept in injector return line tool.
On fuel flowing direction after check-valves, injector return line imports fuel return line.For this reason that strongly
Pressure oscillation also appear on the check-valves in injector return line.There is low-pressure wave, described low in fuel return line
In the case that pressure ripple is also traveled in injector return line, it may occur however that very small such as 0.3bar pressure.In fuel
Standing wave may also occur due to resonant conditions in return line.Due to being sprayed on fuel flowing direction after check-valves
Via non-return valve flow and therefore very small pressure in device return line, check-valves are opened, so as to which therefore fuel can
The pressure on fuel flowing direction before check-valves in injector return line reduces.Therefore, flowed back in injector
Pipeline and therefore also on electromagnetic injection valve device i.e. constant pressure is no longer ensured especially on control room.This causes to spray in magnetic valve
The inaccuracy of the fuel quantity sprayed in emitter and the damage that the part of electromagnetic injection valve device may also be caused.
The A1 of DE 10 2,009 026 596 show the high-pressure pump for trandfer fluid, especially fuel, it include drive shaft,
At least one piston, at least one cylinder for supporting piston, wherein, at least one piston is indirect or is directly supported on
On at least one cam, so as to which the translational motion caused by the rotary motion of drive shaft can be implemented as at least one piston.
The content of the invention
According to the ejector system of the present invention, including at least one injector, the injector includes actuator, by the actuating
Control valve that device manipulates, the injector valve that can be hydraulically manipulated by means of hydraulic coupler by the control valve, at least one it is used for
The reflux opening of hydraulic coupler, the injector return line being connected with least one reflux opening hydraulic pressure guiding,
First check-valve in injector return line, wherein, first check-valve is on fuel flowing direction in injector return line
In be switched on away from least one injector, wherein, second check-valve and second are housed in injector return line
Check-valves is installed relative to first check-valve hydraulic parallel, and second check-valve is returned on fuel flowing direction in injector
Be switched in flow tube road towards at least one injector, so as to using on fuel flowing direction in first check-valve
Pressure oscillation afterwards is improved on fuel flowing direction in the pressure in injector return line before first check-valve
Power.Second check-valve is oppositely constructed relative to first check-valve hydraulic pressure and connected in other words, so as to pass through first check-valve, combustion
Material can only flow on fuel flowing direction away from least one injector, and by second check-valve, fuel is only
It can be flowed on fuel flowing direction along the direction towards at least one injector.In injector return line and because
Also there is strong pressure oscillation in second check-valve in this.It is more than second in the high pressure wave pressure that high pressure half-wave has in other words
During the switching pressure of check-valves, second check-valve is opened, so as to therefore fuel can by second check-valve towards in injector and
The direction flowing of injector return line between second check-valve.Although first check-valve may be due to such as in low pressure half-wave
When such pressure oscillation and open and the therefore fuel of the injector return line between injector and first check-valve
It can be flowed via first check-valve.However, in high pressure half-wave then, first check-valve is closed and second check-valve is beaten
Open, so as to which therefore fuel can be flow in injector and second again by second check-valve in other words between first check-valve
In injector return line.Unintentionally opening lost fuel by first check-valve during low pressure half-wave can be in high pressure half
Supplied again by second check-valve during ripple in injector and the first injector return duct between second check-valve in other words
Road.Accordingly, there exist in the pressure of injector and the first fuel in the injector return line between second check-valve in other words
Fifty-fifty it is held substantially constant in time, pressure is between 1 and 1.5bar.Therefore, in an advantageous manner, injector has
Constant and accurate emitted dose and therefore it can avoid due to the injector between injector and the first and second check-valves
Damage caused by different pressure in return line on the injector.
Injector return line especially has the first branch location and the second branch location, and first check-valve leads to
One and second branch location, and second check-valve leads to the first and second branch locations.
In another configuration, the first branch location and the second branch location are returned with two branch hydraulically separated injectors
Flow tube road is connected with each other, and first check-valve and second check-valve are separately mounted in branch's injector return line.
In the embodiment of a supplement, first check-valve and second check-valve have substantially the same switching pressure.
The difference of the substantially the same switching pressure of first check-valve and second check-valve is less than 5%, 3% or 1%.Here, cut
Such pressure of the pressure for first check-valve and second check-valve is changed, under the pressure, first check-valve in other words second
Check-valves opens and closes.Here, a pressure differential of the switching pressure in particular in first check-valve and/or second check-valve,
So as to which the first and second check-valves are opened when pressure differential is more than the switching pressure, and it is less than the switching in pressure differential and presses
The first and second switch valves are closed during power.
Preferably, first check-valve has significantly bigger switching pressure than second check-valve.The switching of first check-valve
The switching pressure of pressure ratio second check-valve is significantly bigger, i.e., it is bigger by least 5%, 10% than the switching pressure of second check-valve or
15%.Therefore, the combustion with being imported by second check-valve in the injector return line between injector and second check-valve
Material is compared, and less fuel is directed at fuel tank by first check-valve.
In a modification, first check-valve has significantly smaller switching pressure than second check-valve.First check-valve
The switching pressure of switching pressure ratio second check-valve is significantly smaller, so that the switching pressure ratio second check-valve of first check-valve
Switch pressure it is small by least 5%, 10% or 15%.Therefore, with being imported by second check-valve in injector and second check-valve
Between injector return line in fuel compare, more fuel are flowed in fuel tank by first check-valve.
Meet destination, first check-valve and second check-valve for the machine with valve spring and with movable closure member
Tool check-valves.
Meet destination, first check-valve and second check-valve are integrated in common housing.
In another embodiment, first check-valve and second check-valve have substantially the same indicatrix.Such as
The indicatrix flows transversal in other words dependent on the spring constant of valve spring and the geometry of the opening on check-valves
Area.The pressure differential and the volume flow of the associated fuel for flowing through the check-valves that the indicatrix is given on check-valves
Function relevance between amount, wherein, the pressure differential is more than the switching pressure.
In an additional embodiment, first check-valve and second check-valve are configured to electric check-valves.Therefore, by means of
Pressure sensor measures the pressure before and after the valve as check-valves, and in the corresponding switching pressure as pressure differential
In the case of, first check-valve and/or second check-valve electronically, are for example opened and closed by means of magnet respectively.
In another embodiment, hydraulic coupler has control room, the control room can with different pressure-loadeds, and
Reflux opening is led in control room, and reflux opening can especially be opened and closed by means of the control valve.
In a modification, the hydraulic fluid of hydraulic coupler is the fuel sprayed by injector.
At least one injector in particular electromagnetic injection valve device, it has the electromagnet as actuator.
In an additional embodiment, at least one injector is piezoelectric injector, and it, which has, is used as actuator
Piezoelectric element.
In another configuration, the ejector system includes multiple injectors, especially electromagnetic injection valve device, and each spraying
Device respectively has a reflux opening, and the reflux opening is hydraulically connected with injector return line.Herein, it is preferable that only
One first check-valve and second check-valve are hydraulically connected with these injectors respectively.Unlike this, it is or described more
Each attach troops to a unit respectively a first check-valve and second check-valve in individual injector, so as to the injection with multiple injectors
Device system has multiple first check-valves and second check-valve.
Internal combustion engine, the high-pressure injection system particularly for motor vehicle are used for according to the present invention, it includes：With at least one
The high-pressure pump of individual piston, for conveying fuel to high voltage rail；For conveying fuel to the pre- delivery pump of high-pressure pump；For by fuel
It is directed at the high voltage rail of ejector system；Ejector system with least one injector, wherein, the ejector system construction
For ejector system illustrated in the disclosure in this patent.
In the modification of a supplement, the high-pressure pump includes fuel return line, and injector return line leads to height
In the fuel return line of press pump.
In another modification, injector return line and/or fuel return line are led in fuel tank.
In another configuration, high-pressure pump includes only one piston.
In another modification, pre- delivery pump is controllable and/or adjusts the conveying work(of a gear pump and/or the pre- delivery pump
Rate, and/or pre- delivery pump are the electric pre- delivery pump with motor, and/or can be with pre- defeated for example between 3bar and 6bar
Pressurization pressure conveys fuel by the pre- delivery pump.
According to internal combustion engine present invention, particularly for motor vehicle, that there is high-pressure injection system, wherein, high-pressure injection
System is configured to high-pressure injection system illustrated in the disclosure in this patent.
In another configuration, the pre- delivery pump includes motor.
The motor of the pre- delivery pump is especially integrated in the pre- delivery pump, for example, its mode is loaded forever in gear
Long magnet.
Pressure that can be as caused by high-pressure pump in high voltage rail is for example for diesel engine such as 1000 to 3000bar
In the range of, such as gasoline engine between such as 40bar and 400bar.
Brief description of the drawings
Describe the exemplary embodiment of the present invention in detail referring to the drawings.Accompanying drawing is shown：
Fig. 1 is used for the cross section of the high-pressure pump of trandfer fluid,
Fig. 2 rollers and roller boots and the section A-A according to Fig. 1 of drive shaft,
The view of the high-level schematic of Fig. 3 high-pressure injection systems,
Fig. 4 has the highly simplified cross section of the high-pressure pump of pre- delivery pump and ejector system,
The longitudinal section of the check-valves of Fig. 5 closures,
Fig. 6 according to the longitudinal section of the check-valves of Fig. 5 opening,
The cross section of electromagnetic injection valve devices of the Fig. 7 when injector valve is closed,
Fig. 8 is when injector valve is opened according to the cross section of Fig. 7 electromagnetic injection valve device.
Embodiment
Figure 1 illustrates the cross section of the high-pressure pump 1 for conveying fuel.The high-pressure pump 1 be used under high pressure by fuel,
Such as gasoline or diesel oil are delivered to internal combustion engine 39.Pressure it can be in as caused by high-pressure pump 1 between such as 1000 and 3000bar
In the range of.
High-pressure pump 1 has the drive shaft 2 with two cams 3, and the drive shaft implements rotary motion around rotation axis 26.Rotation
Shaft axis 26 are located in Fig. 1 plane of delineation and perpendicular to Fig. 2 plane of delineation.Piston 5 is supported on to be filled as piston guide
Put in 7 cylinder 6, the cylinder is made up of housing 8.Operating room 29 is by cylinder 6, housing 8 and the gauge of piston 5.With inlet valve 19
Access road 22 and led to the exit passageway 24 of outlet valve 20 in operating room 29.Fuel flows into work by access road 22
In room 29, and fuel is flowed out from operating room 29 again under high pressure by exit passageway 24.Such as check-valves of inlet valve 19 is as follows
Construction：Fuel can only flow into operating room 29, and such as check-valves of outlet valve 20 constructs as follows：Fuel can only be from operating room
29 outflows.The volume of operating room 29 changes due to the reciprocating stroke motion of piston 5.Piston 5 is supported on drive shaft 2 indirectly
On.Roller boots 9 with roller 10 are fixed on piston 5 in other words on the end of pump piston 5.Here, roller 10 can be implemented to rotate
Motion, the rotation axis 25 of the rotary motion are located in the plane of delineation according to Fig. 1, and perpendicular to Fig. 2 plane of delineation.Band
There is the drive shaft 2 of at least one cam 3 with axle-rolling surface 4 and roller 10 is with roller-rolling surface 11.
Contact surface 12 of the roller-working face 11 of roller 10 on axle-rolling surface 4 of the drive shaft 2 with two cams 3
Upper rolling.Roller boots 9 are supported in the roller boots bearing arrangement as sliding bearing being made up of housing 8.Spring 27 is in other words
Helical spring 27 is applied pressure on roller boots 9 as the flexible member 28 clamped between housing 8 and roller boots 9, so as to roll
Sub 10 roller-rolling surface 11 is in lasting contact with axle-rolling surface 4 of drive shaft 2.Therefore, roller boots 9 and piston 5
Jointly implement reciprocal stroke motion.Roller 10 is supported in roller boots 9 by sliding bearing structure 13.
In figure 3 with the high-pressure injection system 36 graphically depicted for motor vehicle of high-level schematic, it has high voltage rail
30 or fuel distributor pipe 31.By means of the injector 44 of ejector system 42 by fuel from the fuel point in other words of high voltage rail 30
Orchestration pipe 31 is ejected into the combustion chamber (not shown) of internal combustion engine 39.Fuel is passed through fuel by the pre- delivery pump 35 of electricity from fuel tank 32
Pipeline 33 is delivered to high-pressure pump 1.Here, the driven shaft 2 of high-pressure pump 1 drives and drive shaft 2 is the axle of internal combustion engine 39, such as song
Axle or camshaft.Metering unit 37 controls and/or adjusted the volume that per time unit is directed at the fuel of high-pressure pump 1.High voltage rail 30
For fuel to be directed at into injector 44.Here, do not led back again by fuel return line 34 by the fuel that high-pressure pump 1 needs
Enter in fuel tank 32.
Fig. 4 also shows that high-pressure injection system 36.Lubricating chamber 40 is constructed within the housing 8 of high-pressure pump 1.In lubricating chamber 40
Show that drive shaft 2, roller 10, roller boots 9 (being not shown in Fig. 4) and piston 5 are partially positioned in lubricating chamber 40.Due to
The stroke motion of piston 5, the pressure oscillation of the about sinusoidal of fuel are appeared in lubricating chamber 40 as pressure wave, the pressure wave
Propagated in fuel conduit 34.Because fuel is guided by lubricating chamber 40, these parts 2,5,9 and 10 are lubricated by fuel.Therefore,
Flow channel 43 within housing 8 be present, also, including and the fuel that is added in lubricating chamber 40 by flow channel 43 again
It is exported and fuel tank 32 (Fig. 4) is supplied by fuel return line 34 again after being exported from lubricating chamber 40.In Fig. 4
In, high-pressure injection system 36 shown in figure 3 is more detail subsequently shown in the case of no internal combustion engine 39.Here, with
Shown embodiment is compared in figure 3, and in Fig. 4 in the embodiment of shown detailed description, high-pressure injection system 36 is not
With metering unit 37.In Fig. 4 in shown embodiment, pre- delivery pump 35 be in terms of transmission power it is controllable and/or
It is adjustable and driven by motor 17.Pre- delivery pump 35 is configured to gear pump 14, such as internal gear pump 15 or external gear
Pump 16 and highly simplifiedly show.By pre- delivery pump 35 from the fuel that fuel tank 32 aspirates by pre- delivery pump 35 with such as 4bar
Pre- discharge pressure supplied by the fuel conduit 33 of high-pressure pump 1, that is, supply high-pressure pump 1 access road 22.In addition, by pre- defeated
Send pump 35 convey fuel during the operation of internal combustion engine 39 by overflow valve 41 and the flow channel connected with the overflow valve 41
43 supply lubricating chamber 40 to lubricate such as drive shaft 2, roller 10 and piston 5.After fuel flows through lubricating chamber 40, fuel is again
It is secondary that fuel tank 32 is supplied to by flow channel 43 and fuel return line 34.Thus Castor Oil and also can cooling-part 2,5,
9 and 10.Here, overflow valve 41 constructs as follows：Constant pressure, the i.e. pre- discharge pressure of 4.5bar are before overflow valve 41
Accounted in fuel conduit 33 leading.It is used for here, pre- delivery pump 35 also conveys in addition to for the conveying capacity of the fuel of high-pressure pump 1
Additional fuel quantity lubricating high-pressure pump 1, flowing through the fuel of lubricating chamber 40.In order to be carried in the transmission power of pre- delivery pump 35
The raising of the pressure on the fuel conduit 33 before overflow valve 41, the fuel pressure before overflow valve 41 are avoided in the case of height
During raising for example from 5.5bar pressure, overflow valve 41 additionally, i.e. so provides fuel and passes through overflow valve 41 for a long time
Larger cross-sectional flow area for use, until 4.5bar pressure accounted for again before overflow valve 41 it is leading.In overflow valve
When the pressure in fuel conduit 33 before 41 is less than 4.5bar, overflow valve 41 is closed.Therefore, the fuel before overflow valve 41
In pipeline 33, it can also provide in the case where slightly being fluctuated in the transmission power of pre- delivery pump 35 during internal combustion engine 39 is run
The pre- discharge pressure of substantial constant between 4.5bar and 5.5bar is for using.
The internal combustion engine 39 of motor vehicle has four unshowned stroke pistons.Here, stroke piston limit engine 39
Especially unshowned four combustion chambers.Injected fuel into by means of four electromagnetic injection valve devices 45 as four injectors 44
In the unshowned combustion chamber of internal combustion engine 39.Therefore, fuel under high pressure by pressure duct 55 supply high voltage rail 30, and from
High voltage rail 30 supplies four electromagnetic injection valve devices (Fig. 3 and 4) via four pressure ducts 55.Electromagnetic injection valve device 45 has respectively
Control room 52 and jet chamber 53.The pressure duct 55 of high-pressure pump 1 is led in jet chamber 53, so as to which fuel continues in jet chamber 53
Ground is under high pressure.Here, control room 52 and jet chamber 53 are connected with carrying out fluid guiding by by-pass flow passage 54.In the figure 7
The injector 54 of closure is shown, from can be via in the flowing in combustion chamber of jet chamber 53 without fuel, and figure 8 illustrates opening
Injector 44, so as to jet chamber 53 the flowable unshowned combustion chamber to internal combustion engine 39 of fuel in.
Control valve 48 is manipulated by the electromagnet 47 as actuator 46, so as to which control valve 48 can be in closed position and open position
Moved between putting.Therefore, control valve 48 is by means of controlling valve rod 68 to be connected with electromagnet 47.In the figure 7, control valve 48 is closed,
So as to which the injector return line 57 led to by reflux opening 56 in control room 52 is not connected fluid guiding with control room 52, and
And in addition, by-pass flow passage 54 is opened, so as to which fuel can be flowed in control room 52 from jet chamber 53.Therefore, in the figure in Fig. 7
Also occur in the control room 52 shown with the same high fuel pressure in jet chamber 53, so as to due to as injector nozzle pin
High pressure on the injector valve 49 of valve 50, the fuel in control room 52 apply so big pressure to injector nozzle needle-valve 50
Power, scheming so as to which injector nozzle needle-valve 50 is resisted the power being applied to by injector spring 67 on injector nozzle needle-valve 50 and is in
In closed position shown in 7.In order to open electromagnetic injection valve device 45, that is make injector nozzle needle-valve 50 from scheming
Closed position shown in 7 moves to open position shown in fig. 8, moves control valve 48 by means of electromagnet 47
Into open position shown in fig. 8, so as to therefore on the one hand close by-pass flow passage 54 and therefore there is no fuel can be from
Jet chamber 53 is flowed into control room 52.In addition, in the open position shown in fig. 8 of control valve 48, returned in injector
The connection for carrying out fluid guiding between flow tube road 57 and control room 52 be present, so as to be opened by the backflow of magnetic valve-injector 45
Mouth 56, the fuel in control room 52 under high pressure can be flowed out by injector return line 57.Here, the structure of reflux opening 56
Make as the throttle position with small cross-sectional flow area, so as to which the pressure in injector return line 57 slowly increases.
However, due to the small volume of control room 52, the pressure of fuel under high pressure in control room 52 is because fuel is from backflow
Opening 56 is flowed out in injector return line 57 and promptly reduced, so as to therefore be applied to injector nozzle pin by fuel
The power that pressure on valve 50 no longer meets from the top down to apply in the direction of motion of injector nozzle needle-valve 50 enough is to keep
Injector nozzle needle-valve 50 is in the figure 7 in shown closed position, so as to which therefore injector nozzle needle-valve 50 passes through injector
Spring 67 is moved upward to from closed position shown in the figure 7 in open position shown in fig. 8.In order that injection
Device nozzle needle 50 is moved to from open position shown in fig. 8 in closed position shown in the figure 7, it is only necessary to is borrowed
Helping electromagnet 47 makes control valve 48 move in closed position shown in the figure 7, so as to therefore in control room 52 by
Occur the pressure such as in jet chamber 53 again in the connection that fluid guiding is carried out by means of by-pass flow passage 54, and therefore spray
Injector nozzles needle-valve 50 is resisted is re-moved to basis by the pressure that injector spring 67 is applied on injector nozzle needle-valve 50
In Fig. 7 closed position.Therefore, control room 52, jet chamber 53, by-pass flow passage 54 and control valve 48 are formed for making injector valve
49 hydraulic couplers 51 hydraulically moved indirectly.For by defined function, the injector on injector 44 returns
In flow tube road 57, it is desirable to the constant pressure between 1 and 1.5bar.
Attach troops to a unit respectively an electromagnetic injection valve device 45 (Fig. 3 and 4) for each in four combustion chambers of internal combustion engine 39.Injection
Device return line 57 converges to the injector return line 57 of an injector return line 57 and the convergence in the first branch
The top set of position 60 is two injector return lines 57, that is, branches into Liang Ge branches-injector return line 62.Then, this
Liang Ge branches-injector return line 62 is converged again in the second branch location 61 and the injector return line 57 exists
Led on mouth 66 in the fuel return line 34 of lubricating chamber 40.Fuel return line 34 is led in fuel tank 32.
First check-valve 58 is fitted into or is integrated in one in Liang Ge branches-injector return line 62, and the
Two check-valves 58 are fitted into or are integrated in another branch-injector return line 62.First and second check-valves 58,59 are tool
There is the mechanical check valve of closure member 64, valve spring 63 and valve chest 65.Figure 5 illustrates the first and second check-valves 58,59
Closed position, and figure 6 illustrates the open position of the first and second check-valves 58,59.Valve spring 63 applies pressure and closed
In closing member 64 and pressure differential be more than the first and second check-valves 58,59 switching pressure in the case of, closure member 64 due to
The pressure acted by fuel on closure member 64 carry closed position shown in Figure 5 move to it is shown in figure 6
In the open position gone out.Here, valve chest 65 has the broadening of the plane of delineation perpendicular to Fig. 5 and 6, so as to which therefore fuel can lead to
Cross the first and second check-valves 58,59 to flow in open position shown in figure 6, because fuel is shown in figs. 5 and 6
The closure member 64 can be streamed within the external valve chest 65 of the sectional view gone out.
First and second check-valves 58,59 are oppositely connected.By first check-valve 58, carry out comfortable electromagnetic injection valve device 45
The fuel of injector return line 57 between first check-valve 58 can only be flowed to by first check-valve towards fuel tank 32
Injector return line 57 in.By second check-valve 59, fuel can only flow into second check-valve 59 and electromagnetic injection valve
In injector return line 57 between device 45.
High-pressure pump 1 has only one piston 5.Due to the stroke motion of piston 5, occurs stereomutation in lubricating chamber 40 simultaneously
And therefore also there is strong pressure oscillation.Pressure oscillation with low pressure half-wave and high pressure half-wave passes through fuel return line 34
The first and second check-valves 58,59 are propagated up to injector return line 57.When low pressure half in first check-valve 58 being present
During ripple, first check-valve 58 is opened, so as to which fuel passes through in the arrival injector return line 57 of first check-valve 58 and therefore
Towards fuel tank 32.Therefore, the pressure in the injector return line 57 between electromagnetic injection valve device 45 and first check-valve 58
Power declines.For electromagnetic injection valve device 45 is by defined function, it is desirable to injection of the fuel on electromagnetic injection valve device 45
Constant pressure in device return line 57 is between 1bar and 1.5bar.When on the tunnel of injector return line 57
When high pressure half-wave be present, second check-valve 59 is opened and first check-valve 58 is closed.Therefore, in the case of high pressure half-wave,
The injector return duct that can be directed fuel between electromagnetic injection valve device 45 and second check-valve 59 by second check-valve 59
In road 57.Therefore, from the fuel that injector return line 57 is flowed out by first check-valve 58 and in height during low pressure half-wave
Press and imported during half-wave by second check-valve 59 in injector return line 57, thereby while in the first and second check-valves
Pressure oscillation on 58,59 is big, but on magnetic valve-injector 45 in injector return line 57 1bar to 1.5bar's
Constant pressure accounts for leading.
Generally apparently, there is essential advantage according to the ejector system 42 of the present invention and according to the high-pressure pump 1 of the present invention.Borrow
Help additional second check-valve 59, the second check-valve 59 oppositely hydraulically connects relative to first check-valve 58, can
Injector return duct on electromagnetic injection valve device 45 is supplied fuel during high pressure half-wave by second check-valve 59 again
Road 57.Therefore, although pressure oscillation is strong in fuel return line 34, returned in electromagnetic injection valve device 45 in injector
The substantially constant pressure between 1bar and 1.5bar is appeared on flow tube road 57.Therefore, electromagnetic injection valve device 45 is sprayable
Accurate fuel quantity is into the combustion chamber of internal combustion engine 39, and in addition, therefore electromagnetic injection valve device 45 is operationally reliable.
Claims (17)
1. ejector system (42), including
- at least one injector (44) with least one reflux opening (56),
- the injector return line (57) being connected with least one reflux opening (56) hydraulic pressure guiding,
- the first check-valve (58) in the injector return line (57), wherein, the first check-valve (58) is in fuel
It is switched on flow direction in the injector return line (57) away from least one injector (44),
Characterized in that,
In the injector return line (57) equipped with second check-valve (59) and the second check-valve (59) relative to
Install first check-valve (58) hydraulic parallel, also, the first check-valve (58) and the second check-valve (59)
Oppositely connect, wherein, the second check-valve (59) is on fuel flowing direction in the injector return line (57)
Be switched on towards at least one injector (44), so as to using on fuel flowing direction in the first check-valve
(58) pressure oscillation after come improve on fuel flowing direction before the first check-valve (58) in the injection
Pressure in device return line (57).
2. ejector system according to claim 1,
- characterized in that, the injector (44) include actuator (46), by the actuator (46) manipulate control valve (48),
The injector valve (49) that can be hydraulically manipulated by means of hydraulic coupler (51) by the control valve (48), wherein, it is provided with and is used for
The reflux opening (56) of the hydraulic coupler (51).
3. ejector system according to claim 1 or 2,
Characterized in that,
The injector return line (57) has the first branch location (60) and the second branch location (61), and described first
Check-valves (58) leads to first branch location and the second branch location (60,61), and the second check-valve (59) is logical
To first branch location and the second branch location (60,61).
4. ejector system according to claim 3,
Characterized in that,
First branch location and the second branch location (60,61) and two branch hydraulically separated injector return lines
(62) be connected with each other, be respectively provided with branch's injector return line the first check-valve and second check-valve (58,
59)。
5. ejector system according to claim 1 or 2,
Characterized in that,
The first check-valve (58) and the second check-valve (59) have substantially the same switching pressure.
6. ejector system according to claim 1 or 2,
Characterized in that,
The first check-valve (58) has significantly bigger switching pressure than the second check-valve (59).
7. ejector system according to claim 1 or 2,
Characterized in that,
The first check-valve (58) has significantly smaller switching pressure than the second check-valve (59).
8. ejector system according to claim 1 or 2,
Characterized in that,
The first check-valve and second check-valve (58,59) are with valve spring (63) and with movable closure member (64)
Mechanical check valve (58,59).
9. ejector system according to claim 2,
Characterized in that,
The hydraulic coupler (51) has a control room (52), and the control room can be with different pressure-loadeds, also, the backflow
Opening (56) is led in the control room (52).
10. ejector system according to claim 1 or 2,
Characterized in that,
At least one injector (44) is electromagnetic injection valve device (45), has the electromagnet (47) as actuator (46).
11. ejector system according to claim 1 or 2,
Characterized in that,
The ejector system (42) includes multiple injectors (44), and each injector (44) respectively has a reflux opening
(56), and the reflux opening (56) is hydraulically connected with the injector return line (57).
12. ejector system according to claim 11,
Characterized in that,
The injector (44) is electromagnetic injection valve device (45).
13. for the high-pressure injection system (36) of internal combustion engine (39), it includes
- the high-pressure pump (1) with least one piston (5), for delivering the fuels to high voltage rail (30),
- be used to deliver the fuels to the pre- delivery pump (35) of the high-pressure pump,
- be used to for fuel to be directed at the high voltage rail (30) of ejector system (42),
- the ejector system (42) with least one injector (44),
Characterized in that,
The ejector system (42) is formed according to any one of the preceding claims.
14. high-pressure injection system according to claim 13,
Characterized in that,
The high-pressure pump (1) includes fuel return line (34), and the injector return line (57) leads to the high pressure
In the fuel return line (34) of pump (1).
15. the high-pressure injection system according to claim 13 or 14,
Characterized in that,
The injector return duct (57) and/or the fuel return line (34) are led in fuel tank (32).
16. the high-pressure injection system according to claim 13 or 14,
Characterized in that,
The high-pressure pump (1) includes only one piston (5).
17. the high-pressure injection system according to claim 13 or 14,
Characterized in that,
The high-pressure injection system (36) is the high-pressure injection system (36) for motor vehicle (38).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012224004.7A DE102012224004A1 (en) | 2012-12-20 | 2012-12-20 | High-pressure injection |
| DE102012224004.7 | 2012-12-20 | ||
| PCT/EP2013/074777 WO2014095271A1 (en) | 2012-12-20 | 2013-11-26 | High-pressure injection system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104870801A CN104870801A (en) | 2015-08-26 |
| CN104870801B true CN104870801B (en) | 2017-12-12 |
Family
ID=49667162
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380065742.6A Active CN104870801B (en) | 2012-12-20 | 2013-11-26 | High-pressure injection system |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2935857B1 (en) |
| CN (1) | CN104870801B (en) |
| DE (1) | DE102012224004A1 (en) |
| WO (1) | WO2014095271A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102013218873A1 (en) * | 2013-09-19 | 2015-03-19 | Robert Bosch Gmbh | Fluid delivery system for a fluid |
| GB2551338A (en) * | 2016-06-13 | 2017-12-20 | Delphi Int Operations Luxembourg Sarl | High pressure fuel pump circuit |
| CN106089524B (en) * | 2016-06-14 | 2019-03-19 | 吉林大学 | High pressure co-rail system and parameter optimization method based on genetic algorithm |
| CN111120173B (en) * | 2019-12-31 | 2021-01-15 | 吉利汽车研究院（宁波）有限公司 | High-pressure oil pump fault detection system, high-pressure oil pump fault detection method and vehicle |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2030219B (en) * | 1978-09-26 | 1983-01-06 | Lucas Industries Ltd | Fuel injection nozzles |
| CN1034361C (en) * | 1987-04-03 | 1997-03-26 | 轨道动力机专卖有限公司 | Improved apparatus for delivering fuel to internal combustion engine |
| EP0681100B1 (en) * | 1994-05-06 | 2002-03-27 | Cummins Engine Company, Inc. | System and methods for electronic control of an accumulator fuel system |
| JP3999855B2 (en) * | 1997-09-25 | 2007-10-31 | 三菱電機株式会社 | Fuel supply device |
| DE10205186A1 (en) * | 2002-02-08 | 2003-08-21 | Bosch Gmbh Robert | Fuel injection device for an internal combustion engine |
| AU2003211017A1 (en) * | 2003-02-12 | 2004-09-06 | Robert Bosch Gmbh | Fuel injector pump system with high pressure post injection |
| US6988488B2 (en) * | 2003-04-15 | 2006-01-24 | Visteon Global Technologies, Inc. | Fuel pressure relief valve |
| DE102008000739A1 (en) * | 2008-03-18 | 2009-09-24 | Robert Bosch Gmbh | Pressure holding valve |
| DE102009026596A1 (en) | 2009-05-29 | 2010-12-02 | Robert Bosch Gmbh | High-pressure pump for high pressure injection system for internal combustion engine, particularly for motor vehicle, has drive shaft with cam, piston and cylinder |
| DE102010064185A1 (en) * | 2010-12-27 | 2012-06-28 | Robert Bosch Gmbh | Fuel injection system for an internal combustion engine |
| FI20115126L (en) * | 2011-02-09 | 2012-08-10 | Waertsilae Finland Oy | Fuel injection system |
-
2012
- 2012-12-20 DE DE102012224004.7A patent/DE102012224004A1/en not_active Withdrawn
-
2013
- 2013-11-26 CN CN201380065742.6A patent/CN104870801B/en active Active
- 2013-11-26 WO PCT/EP2013/074777 patent/WO2014095271A1/en active Application Filing
- 2013-11-26 EP EP13795775.9A patent/EP2935857B1/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN104870801A (en) | 2015-08-26 |
| DE102012224004A1 (en) | 2014-06-26 |
| WO2014095271A1 (en) | 2014-06-26 |
| EP2935857B1 (en) | 2016-09-07 |
| EP2935857A1 (en) | 2015-10-28 |
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