CN104981605B - Valve - Google Patents
Valve Download PDFInfo
- Publication number
- CN104981605B CN104981605B CN201380072317.XA CN201380072317A CN104981605B CN 104981605 B CN104981605 B CN 104981605B CN 201380072317 A CN201380072317 A CN 201380072317A CN 104981605 B CN104981605 B CN 104981605B
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- China
- Prior art keywords
- valve
- pressure pump
- gap
- overflow valve
- fuel
- Prior art date
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- 239000012530 fluid Substances 0.000 claims abstract description 23
- 239000000446 fuel Substances 0.000 claims description 120
- 230000001050 lubricating effect Effects 0.000 claims description 30
- 238000007789 sealing Methods 0.000 claims description 22
- 238000002485 combustion reaction Methods 0.000 claims description 18
- 230000033001 locomotion Effects 0.000 claims description 18
- 238000002347 injection Methods 0.000 claims description 13
- 239000007924 injection Substances 0.000 claims description 13
- 238000004891 communication Methods 0.000 claims description 5
- 239000003502 gasoline Substances 0.000 claims description 4
- 239000002283 diesel fuel Substances 0.000 claims description 3
- 238000010992 reflux Methods 0.000 claims description 2
- 239000002828 fuel tank Substances 0.000 description 9
- 238000005096 rolling process Methods 0.000 description 9
- 239000013589 supplement Substances 0.000 description 9
- 239000000463 material Substances 0.000 description 5
- 230000010355 oscillation Effects 0.000 description 5
- 239000004033 plastic Substances 0.000 description 5
- 229920003023 plastic Polymers 0.000 description 5
- 230000005540 biological transmission Effects 0.000 description 4
- 238000010276 construction Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 230000003534 oscillatory effect Effects 0.000 description 3
- 208000031481 Pathologic Constriction Diseases 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000003139 buffering effect Effects 0.000 description 2
- 230000002045 lasting effect Effects 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000005507 spraying Methods 0.000 description 2
- 208000037804 stenosis Diseases 0.000 description 2
- 230000036262 stenosis Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 239000004411 aluminium Substances 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000009514 concussion Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000003365 glass fiber Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 239000000047 product Substances 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000004804 winding 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
- 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
- F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
-
- 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
-
- 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
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
Valve (42) especially overflow valve (41), for being arranged in high pressure pump case gap, including：It is equipped with the valve chest (45) of valve barrel (44)；The closure piston (46) movable between a closed position and a open position in valve barrel (44), valve (42) is closed in closed position and valve (42) is opened in open position；For fluid input to be surrounded to the inlet opening (47) in cylinder space (56) by valve barrel (44)；At least one outflow opening (49) for discharge input cylinder space (56) interior fluid；The elastic valve member (51) being connect with closure piston (46) especially valve spring (52), valve spring applies closure piston (46) pressure against the pressure applied by the fluid in cylinder space (56) to closure piston (46), it turns off piston (46) to move between a closed position and a open position by the pressure for being applied to closure piston (46) by elastic valve member (51) and fluid, there is no fixing device especially screw thread or plug connection on the outside of valve chest (45).
Description
Technical field
The present invention relates to a kind of valve, a kind of high-pressure pump and a kind of high-pressure injection systems.
Background technology
In the high-pressure injection system of internal combustion engine, particularly in diesel engine or the joint-track type spraying system of gasoline engine
In, high-pressure pump is enduringly responsible for the pressure in the high pressure accumulator for maintaining joint-track type spraying system.For example, high-pressure pump can pass through
The camshaft of internal combustion engine is driven by means of drive shaft.In order to deliver fuel to high-pressure pump, pre- delivery pump (such as tooth has been used
Wheel pump or rotary vane pump), these pre- delivery pumps are preposition in high-pressure pump.Fuel is passed through fuel by pre- delivery pump from fuel tank
Pipeline transport is to high-pressure pump.
In addition, using piston pump as high-pressure pump.It is supported with drive shaft in the housing.Piston is relative to drive shaft radial direction
Ground is arranged in cylinder.The idler wheel of outfit idler wheel-rolling surface, the idler wheel branch are mounted on the drive shaft of at least one cam is equipped with
It holds in roller mount.Roller mount is connect with piston, so as to make piston positive into oscillatory type translational motion.Spring applies roller mount
The power being radially directed towards relative to drive shaft, so as to which idler wheel be made to be contacted always with drive shaft.Idler wheel is with idler wheel-rolling surface in axis-rolling
It is in and contacts with drive shaft on dynamic face (surface as the drive shaft at least one cam).Idler wheel is by means of slidably supported
Portion is supported in roller mount.
Herein, the drive shaft at least one cam, the idler wheel and the roller mount is arranged on high-pressure pump
Lubricating cavity in.The fuel that high-pressure pump is delivered to by pre- delivery pump is guided by this lubricating cavity, on the one hand to lubricate the profit
The component in sliding intracavitary portion, also, these components are cooled down with flowing through the fuel of lubricating cavity.Therefore, it is delivered to by pre- delivery pump
On the one hand the fuel of high-pressure pump includes the fuel for flowing through lubricating cavity in terms of volume flow, for lubricating and cooling down positioned at lubricating cavity
Internal high pressure pump part and specified fuel for high-pressure pump is further comprised, to be delivered to high voltage rail under high pressure.
Here, the pressure substantial constant on the fuel conduit from pre- delivery pump to high-pressure pump.For this reason, it is conveyed from pre-
Pump is equipped with overflow valve to lubricating cavity or from lubricating cavity to the flow channel of fuel tank.Overflow valve is arranged on high pressure pump case
Inside gap.When higher than setting pressure (such as 5.5bar), overflow valve is opened, also, thus passes through more fuel guiding
Lubricating cavity, also, these guiding are supplied again by the fuel of lubricating cavity to fuel tank.During pressure reduction before overflow valve,
During such as less than 4.5bar, overflow valve is closed.
This overflow valve has valve barrel and closure piston, and the closure piston is movable between closed position and open position
Ground is supported on cylinder.Fuel can be flowed into overflow valve by inlet opening and be flowed out by outflow opening from overflow valve.
On the one hand, the fuel pressure at inlet opening and a spring act on closure piston.That herein, closure piston is acted on,
The power being placed in by spring under pressure and the power being placed under pressure by fuel are negative directions, so as to the fuel at inlet opening
Piston is turned off in the case of pressure difference to move in cylinder interior.Herein, the outflow opening in cylinder space surrounded by cylinder is led to
It is closed when closure piston is in the closed position.Pressure only at inlet opening by fuel come when improving, closure piston
It just moves in open position, in the open position, the outflow opening at cylinder space is not closed piston closing.
Cylinder space is closed piston and is divided into the first sub- cylinder space and the second sub- cylinder space as spring cavity.In the second son
Spring cavity is interior equipped with spring in other words, also, compensates opening and led in spring cavity across valve barrel in cylinder space.In normal operation,
Spring cavity is with filling fuels, also, compensation opening can move back and forth for turning off piston, because back and forth being transported in closure piston
The volume of spring cavity changes when dynamic.Herein, compensation opening turns off reciprocating motion of the pistons together with spring cavity and is buffered,
Because be closed the fuel that piston squeezes in spring cavity only can become hour by compensating opening outflow in the volume of spring cavity
Then in turn.Not or with small return pressure in the fuel return line from high-pressure pump (or lubricating cavity) to fuel tank
Fuel return line in, it may occur that spring cavity empty or lubricating cavity inflation.As a result, it is put into operation again in high-pressure pump again
Afterwards, closure piston in longer period of time or always that the fuel inside the spring cavity does not occur caused by buffering, this can
It can result in closure piston vibration and thus cause noise generation and additional mechanical load or overflow valve abrasion.
10 2,009 026 596 A1 of DE give a kind of high-pressure pump for being used for trandfer fluid, particularly fuel, including
Have drive shaft, at least one piston, at least one cylinder for supporting piston, wherein, at least one piston indirectly or
It is directly supported at least one cam, so as to make at least one piston that can implement due to drive shaft rotary motion
Translational motion.
Invention content
Valve, particularly overflow valve according to the invention, for being arranged in the gap of high pressure pump case, which includes：Match
The valve chest of standby valve barrel；The closure piston that can be moved between closed position and open position inside valve barrel, so as to which valve be made to exist
It is closed in closed position and valve is made to open in the open position；Inlet opening, for applying the fluid to what is surrounded by valve barrel
Cylinder space interior；At least one outflow opening, for the fluid discharge in input cylinder space will to be imported into；It is connect with closure piston
Elastic valve member, particularly valve spring, using the valve spring can to closure piston apply pressure, this pressure reversal in by cylinder sky
Between the internal fluid pressure that can apply to closure piston orient, so as to which closure piston is by means of by elastic valve member and by fluid
Pressure on be applied to closure piston and can be moved between closed position and open position, wherein, valve chest on the outside on
Without or for fixed fixing device axial in the gap at high pressure pump case, particularly without screw thread do not have
Plug connection.On valve chest, on the outside on be not configured with for fixed fixation axial in the gap at high pressure pump case
It device, particularly is not configured with screw thread or is not configured with external screw thread.Intermediate cavity between valve chest and high pressure pump case as a result,
It is flowed through in the axial direction by fluid.Herein, valve is axially fixed in inside housing gap and be generally accomplished by the following way：It is logical
Cross the placement on the first inner end and/or the second outer end of valve；And/or the peace by the sealing ring on the seal groove on valve
It puts；And/or by the placement on the slot (particularly seal groove) on valve chest outside, wherein, the placement of the valve or valve chest
It is realized on the housing of high-pressure pump.In contrast to this, on valve chest can also on the outside on be configured with annular protrusion, be used for
It is valve is axially disposed and be fixed in high pressure pump case.
In an additional form of implementation, cylinder space is closed piston and is divided into the first sub- cylinder space and the second sub- cylinder sky
Between, also, the inlet opening and at least one outflow opening are led in the first sub- cylinder space, also, elastic valve member is set
It puts in the second sub- cylinder space interior as spring cavity, and compensates opening and particularly radial lead to the second sub- cylinder across valve chest
In space.
In one is supplemented variant scheme, on the longitudinal axis direction of valve, only in inlet opening and at least one outflow
Between opening, (it is particularly on the outside) at valve chest and is configured with and/or is provided with seal groove and/or sealing ring.Except this it
Outside, on valve between inlet opening and at least one outflow opening, therefore valve can be in the situation in being set to housing gap
Under on the outside on by fluid winding flow.
The high-pressure pump according to the invention for being used to convey fuel (such as diesel oil or gasoline), including：Housing；It is equipped at least
The drive shaft of one cam；At least one piston, for conveying fuel；At least one cylinder, for supporting at least one piston；
Here, at least one piston is supported on indirectly in the drive shaft at least one cam, so as to make at least one piston due to
The rotary motion of drive shaft and translational motion can be carried out；Lubricating cavity；The gap of construction inside housings, for setting overflow
Valve；The overflow valve being arranged on inside gap, with inlet opening and at least one outflow opening, wherein, gap has first
Inner end and the second outer end, second outer end in gap are used for fuel guiding as flow channel through lubricating cavity, and
It is preferred for exporting fuel from gap.Therefore, fuel can be guided by the second outer end of gap, and thus with advantageous
Mode also makes intermediate cavity between valve chest and high pressure pump case since at least one outflow opening towards overflow valve
Second outer end direction is flowed through by fuel, also, the air in this intermediate cavity thus is passed through importing on the second outer end
Fuel is particularly simply removed by means of guiding fuel by intermediate cavity.
In the form of implementation of a supplement, a gap flow channel is led in gap, also, in gap longitudinal axis side
Upwards, compared at least one outflow opening of overflow valve, inlet opening to the gap flow channel of overflow valve is led in gap
Communication port to have smaller spacing and/or pore structure be hole.Fuel can imported into gap by gap flow channel
It is interior, also, allowed the fuel to since first inner end in gap up to this section of the inlet opening of overflow valve from gap
Flow channel is imported into across gap in the inlet opening of overflow valve.
Appropriately, sealing ring is configured between high pressure pump case and overflow valve, further, it is preferred that sealing ring is in sky
It is oriented between inlet opening and at least one outflow opening on the longitudinal axis direction of gap.Sealing ring divides gap
Into：First sub- gap, from the first inner end of gap up to sealing ring；Second sub- gap, from sealing ring up to the second outer end of gap
Portion.Herein, the first and second sub- gaps prevent fluidly sealing with sealing ring, also, can only be made by opening overflow valve
Fuel is guided from the first sub- gap to the second sub- gap.
In an additional variant scheme, it is equipped in the region of second outer end in gap and takes over, particularly flow back
It takes over, there is the take over channel inside gap, also, take over channel is used to guide fuel.
In the configuration of a supplement, the outer axial end portion of overflow valve, which is placed in, to be taken over, and thus overflow valve is made to exist
It is fixed in gap on axial direction.Second outer end of overflow valve (particularly valve chest), which is placed in, to be taken over, and thus
Overflow valve can be made to be fixed in gap in the axial direction.Herein appropriately, overflow valve in the axial direction additionally with
Sealing ring is placed on the housing of high-pressure pump, and thus valve can be made to be fixed on the shell of high-pressure pump on above-mentioned two axial direction
On body.
In the configuration of a supplement, take over and connected inside gap by means of the housing of press-fit connecting portion and high-pressure pump
It connects.It can make to take over extremely simple in high pressure pump case by means of press-fit connecting portion and reliably mechanically be fixed in gap
Portion, also, thus also additionally can prevent fluidly closing second outer end in the gap, so as on second outer end in gap
It is only capable of fuel being made to come out from gap by take over channel.
In the variant scheme of a supplement, the overflow valve of high-pressure pump is configured in overflowing illustrated in this protection application
Flow valve.
Appropriately, on the axial direction of overflow valve, in the outflow opening of overflow valve and the outer axial end portion of overflow valve
Between, intermediate cavity is configured with and (is especially ring-shaped) between valve chest and the housing of high-pressure pump, for fuel to be opened from outflow
Mouth is guided to the outer axial end portion of overflow valve and is preferably guided to the second end in gap.When closure piston is opened, fuel
It can be flowed by the inlet opening of valve in the first sub- cylinder space and be opened from the first sub- cylinder space by least one outflow
Mouth is flowed into intermediate cavity.And then, from the fuel that at least one outflow opening comes out on the outside on axially (also
It is to say, on the longitudinal axis direction of valve) it is streamed from the second outer end of the first inner end to the overflow valve of overflow valve positioned at valve
Overflow valve between housing and high pressure pump case.
In an additional form of implementation, the swept volume of valve piston is more than the volume of intermediate cavity.The stroke of valve piston holds
Product is the volume in the first and/or second sub- cylinder space, and the closing which squeezes between an open position and a closed is lived
Plug.
In the variant scheme of a supplement, intermediate cavity is divided into empty as second of spring cavity cylinder positioned at leading to
The sub- intermediate cavity of axial direction between interior compensation opening and the outer axial end portion of overflow valve, also, the swept volume of valve piston is big
In the volume of sub- intermediate cavity.From the second sub- cylinder space, spring cavity leads to valve chest and high pressure to compensation opening on valve chest in other words
Intermediate cavity between pump case.It therefore, can be by closure piston in open position and closing for the air in sub- intermediate cavity
Moving to move back and forth in other words between position makes entire sub- intermediate cavity fill fuel.As long as make son when high-pressure pump turns off as a result,
Intermediate cavity, just can be particularly safe and reliably intermediate with filling fuels at least partly (particularly fully) full of air
Chamber.Therefore, when high-pressure pump puts into operation again, sub- intermediate cavity (particularly intermediate cavity) particularly simply can also fill combustion again
Material, and thus closure piston will not be caused to vibrate because the second sub- cylinder space in other words spring cavity can it is thus extremely simple and
Reliably fuel is filled by compensating opening again.
In the variant scheme of a supplement, the inlet opening of overflow valve is constructed on the interior axial end portion of overflow valve.
It is according to the invention to be used for internal combustion engine, particularly the high-pressure injection system for motor vehicle, include：With lubrication
The high-pressure pump of chamber and overflow valve；Pre- delivery pump；High voltage rail；Wherein, overflow valve is configured to illustrated in this protection application
Overflow valve and/or high-pressure pump are configured in the high-pressure pump illustrated in this protection application.
In the form of implementation of a supplement, spring retainer, also, the spring retainer and elasticity are equipped in valve barrel
Valve member connects.
Preferably, elastic valve member is arranged in cylinder space.
Appropriately, at least one outflow opening be closed in the closed position of closure piston piston closing and/or extremely
A few outflow opening is led in the open position of closure piston in the first sub- cylinder space.
In another form of implementation, compensation opening is led in the second sub- cylinder space, for directing fluid into and exporting second
Sub- cylinder space.Compensation is open to direct fuel to and export the second sub- cylinder space.When closure piston moves, the second sub- cylinder is empty
Between volume change.It can be moved to mainly turn off piston, in the case where fuel is incompressible it is required that passing through
Compensation opening with very little flow cross section also can direct fluid into and export the second cylinder space.Herein, in inlet opening
Place may also can cause pressure oscillation.It is this particularly the short time pressure oscillation may result in closure piston oscillation or
Vibration motion.It is filled (particularly with liquid (particularly fuel) with reduced size and the second sub- cylinder space in compensation opening
It is filled up completely) in the case of, thus, it is possible to react on this concussion of the closure piston caused by pressure oscillation in other words
Faster reciprocal motion, also, merely due to the lasting pressure change of liquid in inlet opening, just buffering ground is slowly for closure piston movement
Speed carries out, and is not in that closure piston is vibrated and thus drawn thus when filling liquid (particularly fuel) in the second sub- cylinder space
The noise generation risen and mechanical wear.
In the variant scheme of a supplement, at least one outflow opening leads to the second sub- cylinder space, particularly leads to pass
Close the entire position of piston.
In another configuration, valve include at least partly, particularly fully by metal, such as steel or aluminium and/or by
Plastics are made.Metal is for manufacturing the durable of valve and lasting material.Plastics have lighter weight in an advantageous manner
Amount, and thus making the very light in weight of valve.Herein, the plastics of glass fiber reinforcement are preferably related in the case of plastics.
Preferably, valve chest and/or closure piston and/or spring retainer be at least partly, particularly fully in other words for valve barrel
It is made of plastics.
In the scheme of a supplement, the volume of fuel stream of high-pressure pump is delivered between the internal combustion engine runtime from pre- delivery pump
Controllable and/or adjustable, mode is to control and/or regulate the transmission power of the pre- delivery pump, alternatively, single using metering
Member controls and/or regulates the flow cross section of the flow channel from pre- delivery pump to high-pressure pump.If pre- delivery pump is conveying
It is controllable or adjustable in terms of power, then metering units are not needed to, also, guide the volume of fuel to high-pressure pump fluently with pre-
Delivery pump controls and/or regulates.If pre- delivery pump is uncontrollable and/or unadjustable in terms of transmission power, this profit
Implemented with metering units.
In another configuration, pre- delivery pump includes motor.
Specifically, the motor of pre- delivery pump is integrated into pre- delivery pump, and mode is, for example, to be encased in permanent magnet
In gear.
By high-pressure pump can in high voltage rail generated pressure, such as diesel engine, in 1000bar extremely
In the range of 3000bar, alternatively, for example for gasoline engine, in 40bar between 400bar.
Description of the drawings
The embodiment of the present invention is illustrated below according to affiliated attached drawing.It is shown in attached drawing：
Fig. 1：For the high-pressure pump drawing in side sectional elevation of trandfer fluid,
Fig. 2：The A-A sectional views according to Fig. 1 of idler wheel and drive shaft with roller mount,
Fig. 3：The strong schematic representation of high-pressure injection system,
Fig. 4：The drawing in side sectional elevation simplified by force of high-pressure pump with pre- delivery pump,
Fig. 5：The profilograph for the overflow valve being known from the state of the art,
Fig. 6：The profilograph of overflow valve according to the invention,
Fig. 7：The profilograph of high pressure pump case, the high pressure pump case have overflow according to the invention in housing gap
Valve.
Specific embodiment
Be shown in FIG. 1 for convey fuel high-pressure pump 1 drawing in side sectional elevation.High-pressure pump 1 is used for fuel (such as vapour
Oil or diesel oil) it is delivered to internal combustion engine 39 under high pressure.The pressure that can be generated by high-pressure pump 1 for instance in 1000bar extremely
In the range between 3000bar.
High-pressure pump 1 has the drive shaft 2 for being equipped with two cams 3, which implements rotary motion around rotation axis 26.
Rotation axis 26 is located in the plan of Fig. 1 and perpendicular to the plan of Fig. 2.Piston 5 is supported in cylinder 6, and the cylinder is by housing 8
It is formed.Working chamber 29 is by 5 gauge of cylinder 6, housing 8 and piston.With into valve 19 into channel 22 and with bleeder 20
Channel 24 is released to lead in working chamber 29.Fuel is flowed by the opening that enters entered on channel 22 in working chamber 29, also,
Fuel under high pressure is flowed out by releasing the opening of the releasing on channel 24 23 from working chamber 29 again.(such as stop into valve 19
Return valve) it forms as follows：Fuel can be only flowed into working chamber 29, also, bleeder 20 (such as check-valves) is formed as follows：Combustion
Material can only be flowed out from working chamber 29.Since 5 oscillatory type of piston moves back and forth, the volume variation of working chamber 29.Piston 5 is indirectly
Support is on driving shaft 2.The roller mount 9 for being equipped with idler wheel 10 is fixed on the end of piston 5 (pump piston 5 in other words).At this
In, idler wheel 10 can implement rotary motion, and the rotation axis 25 of the idler wheel is located in the plan according to Fig. 1 and perpendicular to figure
2 plan.Being equipped with the drive shaft 2 of at least one cam 3 has axis-rolling surface 4, also, idler wheel 10 has idler wheel-rolling surface
11。
Idler wheel-rolling surface 11 of idler wheel 10 has axis-rolling of above-mentioned two cam 3 on contact surface 12 in drive shaft 2
It is rolled on face 4.Roller mount 9 is supported in the roller mount supporting part as sliding supporting part being made of housing 8.Housing 8 with
It is being clamped between roller mount 9, as the spring 27 of elastic component 28, helical spring 27 pressure is applied in roller mount 9 in other words,
It is contacted always with axis-rolling surface 4 of drive shaft 2 so as to idler wheel-rolling surface 11 of idler wheel 10.Therefore, roller mount 9 and piston 5 are common
With implementation oscillatory type reciprocating motion.Idler wheel 10 is supported on sliding supporting part 13 in roller mount 9 together.
Illustrate to show the high-pressure injection system 36 for motor vehicle to be not shown with strong in figure 3, with high voltage rail
30 or fuel rail 31.Fuel is injected to internal combustion engine 39 by means of valve (not shown) from high voltage rail 30 or fuel rail 31
Combustion chamber (not shown) in.Fuel is delivered to high-pressure pump 1 by electronic pre- delivery pump 35 from fuel tank 32 by fuel conduit 33.
Herein, 1 driven shaft 2 of high-pressure pump drives, also, drive shaft 2 is the axis (such as bent axle or camshaft) of internal combustion engine 39.Meter
Amount unit 37 controls and/or regulates the volume of fuel guided per unit time to high-pressure pump 1.High voltage rail 30 is used to inject fuel into
Into the combustion chamber of internal combustion engine 39.Herein, the 1 unwanted fuel of institute of high-pressure pump is drawn again by optional fuel return line 34
It is directed back in fuel tank 32.
Fig. 4 shows a part for high-pressure injection system 36.There is lubricating cavity 40 in 8 internal structure of housing of high-pressure pump 1.
Drive shaft 2, idler wheel 10, roller mount 9 (being not shown in Fig. 4) are equipped in lubricating cavity 40 and is partially provided with piston 5.Passing through will
Fuel is directed through lubricating cavity 40, these components 2,5,9 and 10 is made to be lubricated by fuel.For this purpose, it is logical to be internally provided with flowing in housing 8
Road 43, also, fuel is flowed into lubricating cavity 40 by the flow channel 43 and is then flowed out again from the lubricating cavity, also,
It is supplied again to fuel tank 32 (Fig. 4) by fuel return line 34 after being flowed out from lubricating cavity 40.It is shown in detail in Fig. 4
The high-pressure injection system 36 shown in Fig. 3, without showing high pressure-rail 30 and internal combustion engine 39.Herein, with showing in Fig. 3
Unlike embodiment, the high-pressure injection system 36 in the specific embodiment being shown in FIG. 4 does not have metering units 37.Scheming
In the embodiment shown in 4, pre- delivery pump 35 is controllable and/or adjustable in terms of transmission power, and the pre- delivery pump leads to
Motor 17 is crossed to drive.Pre- delivery pump 35 is configured to gear pump 14 (such as internal gear pump 15 or external gear pump 16) and strong letter
It shows with changing.By pre- delivery pump 35 from the fuel that fuel tank 32 aspirates by the pre- delivery pump with pre- discharge pressure (such as 4bar)
35 are supplied by fuel conduit 33 to high-pressure pump 1 (that is, supply enters valve 22 to high-pressure pump 1).In addition to this, inside
During the operation of combustion engine 39, the fuel that is conveyed by pre- delivery pump 35 by overflow valve 41 and is placed on after lubricating cavity 40 is flowed through
The flow channel 43 of overflow valve 41 is flowed out from lubricating cavity 40, to lubricate such as drive shaft 2, idler wheel 10 and piston 5.In The fuel stream
After lubricating cavity 40, fuel is supplied further through flow channel 43 and fuel return line 34 to fuel tank 32.These portions as a result,
Part 2,5,9 and 10 can be lubricated and can be also cooled.Herein, overflow valve 41 is formed as follows, in 41 front of overflow valve
Fuel conduit 43 in and lead in the fuel conduit 43 in lubricating cavity 40 that there are constant pressure (that is 4.5bar
Pre- discharge pressure).Herein, other than being used for the fuel delivery of high-pressure pump 1, pre- delivery pump 35 also conveys to lubricate this
The amount of extra fuel (that is, flowing through the fuel of lubricating cavity 40) of high-pressure pump 1.It is conveyed in order to avoid being improved in pre- delivery pump 35
Pressure rise during power at the fuel conduit 33 of 41 front of overflow valve, the fuel pressure in 41 front of overflow valve increase (example
Such as from 5.5bar pressure) when overflow valve 41 is additionally opened, that is to say, that provide fuel by the larger stream of overflow valve 41
Dynamic cross section, the pressure before overflow valve is again for until 4.5bar.Pressure in the fuel conduit 33 of 41 front of overflow valve
When power is less than 4.5bar, overflow valve 41 is closed.As a result, during internal combustion engine 39 is run, the fuel conduit in 41 front of overflow valve
4.5bar is capable of providing in 33 to the pre- discharge pressure of substantial constant between 5.5bar, even if in the conveying work(of pre- delivery pump 35
Volume flow of the rate with reference to needed for high-pressure pump 1 is also such in the case of slightly fluctuating.
Overflow valve 41 of the valve 42 well known in the prior art as high-pressure injection system 36 is shown in FIG. 5.Overflow valve
41 have valve chest 45, and the valve chest is to 44 gauge of valve barrel.Screw thread 60 is configured on the outside of valve chest 45 as external screw thread
60, which forms fixing device 38, for being axially fixed in inside gap 61 on the housing 8 of high-pressure pump 1.In valve barrel 44
Portion is supported with closure piston (Schlie β kolben) 46.Due to the sliding supporting part on valve barrel 44, closure piston 46 can be implemented
It is axially moved, that is to say, that according to Fig. 6 diagrams from left to right and vice versa.Valve barrel 44 or valve chest 45 enclose cylinder space
56.Herein, cylinder space 56 is closed piston 46 and is divided into the first sub- 57 and second sub- cylinder space 58 of cylinder space.For fluid
The inlet opening 47 of (particularly fuel) is led in the first sub- cylinder space 57, because being machined with flow channel in valve chest 45
48.Herein, flow channel 48 is constructed in the axial direction in valve chest 45.In addition to this, two outflow openings 49 are led to
In first sub- cylinder space 57, because there are two the flow pass 50 of radial direction for processing in valve chest 45.Closure piston 46 is (in other words
Half sphere shape 46) it is supported on valve barrel 44 by means of sliding supporting part in the axial section with larger diameter or radius.
On the second section, closure piston 46 has smaller diameter, also, in this section right part region with small diameter
Interior, closure piston 46 has seal receptacle 54.
Valve spring 52 is equipped in the second sub- cylinder space 58 as elastic valve member 51.Herein, elastic valve member 51 is at one end
On be fixed on the spring retainer 53 of fastening, be fixed on an opposite end on closure piston 46.Spring retainer 53 encloses
It valve barrel 44 and is configured to independent component and is complemented at valve chest 45.Unlike herein, spring retainer 53 can also be with valve casing
Body 45 is integrally formed (not shown).On on the outside, there are two seal grooves 62 for construction on valve chest 45, are set respectively in these slots
There is sealing ring 63 (such as elastic rubber sealing element).Valve chest 45 can be integrated by means of sealing ring 63 or be encased in as a result,
In the housing 8 of high-pressure pump.For this purpose, hole 64 that the housing 8 of high-pressure pump 1 is constructed with respective complementary or with as gap 61
Opening, sealing ring 63 is placed in the hole or opening, and flow channel 43 is thus enable to be directed across flow channel 48
With above-mentioned two flow pass 50.
The outs open position of closure piston 46 is shown in FIG. 5.In this outs open position, above-mentioned two stream
Go out 49 parts of opening and be closed piston 46 with the closing of larger-diameter section, can partly enable flow through above-mentioned two outflow
Opening 49 is flowed out from the first sub- cylinder space 57.Herein, fluid (particularly fuel) is flowed into the first son by flow channel 48
In cylinder space 57.If the fuel pressure in the first sub- cylinder space 57 continues to improve (such as being increased to exceed the value of 5bar),
Piston 46 is then turned off due to the fuel pressure in the first sub- cylinder space 57 is larger and is pressed against and is applied by valve spring 52
Pressure continue to left movement, so as to therefore above-mentioned two flow pass 50 is made to continue to open.When dropping under stress, closure piston
46 move right so far, (enclose lead to the first sub- cylinder sky in other words into channel 48 until seal receptacle 54 has been completely enclosed
Between inlet opening 47 in 57) until.During closure piston 46 moves, the volume in the second sub- cylinder space 58 also changes.It is closing
Closing piston 46 has there are small gap between larger-diameter section and valve barrel 44, so as in very small region
Fuel is made also to reach the second sub- cylinder space 58 from the first sub- cylinder space 57.Therefore, as long as the second sub- 58 (spring in other words of cylinder space
Chamber 58) without being full of air, then therefore the second sub- cylinder space 58 is filled with due to the slight pressure in fuel return line 34
Substantially incompressible fuel.It is moved to can mainly turn off piston 46, then it is required that in the second sub- cylinder space 58
Interior fuel can be flowed outwardly from the second sub- cylinder space 58 by compensation opening 59 and be flowed into again.Herein, compensation opening
59 have very small diameter or small flow cross section (such as diameter is in the range between 0.5mm to 1mm).As a result,
The pressure oscillation of fuel in 47 region of inlet opening will not cause closure piston 46 to vibrate, because making combustion by compensating opening 59
Material only slowly flows in and out the second sub- cylinder space 58, and thus the fuel only in 47 region of inlet opening is in quite long-term
46 kicking motion of closure piston can just be caused during pressure change.Seal receptacle 54 can be in an advantageous manner in the closing of closure piston 46
Overflow valve 41 is fully sealed in position.
The profilograph of overflow valve 41 according to the invention is shown in FIG. 6.Substantially only illustrate below with showing in Fig. 5
The difference of the overflow valve 41 of the prior art gone out.Valve chest 45 is upper on the outside not to have screw thread as valve chest 45 is axial
The fixing device being fixed on 1 housing 8 of high-pressure pump.Therefore, overflow valve 41 according to the invention can not axially,
That is not along the direction of the longitudinal axis 77 of valve 42 or the longitudinal axis 77 in the gap 61 for being configured to hole 64 in the axial direction
On be fixed on the housing 8 of high-pressure pump (Fig. 7).It is close on the seal groove 62 of valve chest 45 in order to by 41 axial restraint of overflow valve
Seal 63 is placed on the flange 78 of 1 housing 8 of high-pressure pump.Valve 42 has the first inner end 72 and the second outer end 73.In overflow
The take over 68 for being configured to reflux take over 69 is mounted on second outer end 73 of valve 41.Take over 68 is by means of press-fit connecting portion
(Pressverbund) 71 with the housing 8 of high-pressure pump 1 with realizing Fluid Sealing and force closure connect.
As already mentioned, the gap 61 for being configured to hole 64, gap tool are machined in the housing 8 of high-pressure pump 1
There is longitudinal axis 77.Hole 64 has the first inner end 65 and the second outer end 66.Since the second outer end 73 of overflow valve 41 is pacified
It puts on the end of take over 68 and sealing ring 63 is placed on the flange 78 of housing 8, therefore valve 42 is fixed in the axial direction
Inside hole 64.Overflow valve 41 according to the invention is only between above-mentioned two outflow opening 49 and inlet opening 47 in overflow valve
There is sealing ring 63, so as to therefore make the intermediate cavity 74 along 77 direction of longitudinal axis (from above-mentioned on 41 the first inner end 72
Two outflow openings 49 or since sealing ring 63 up to the second outer end 73 of overflow valve 41) energy when closure piston 46 is opened
It is enough to be flowed through by the fuel flowed out from above-mentioned two outflow opening 49.On the end of take over 68 being set to inside hole 64, construction
There are multiple radial direction take over slots 76, the fuel so as to enable to flow through intermediate cavity 74 is in the region of the second outer end 73 of overflow valve 41
It is interior that by these, radially take over slot 76 flow to take over channel 70 in radial directions.Due to the sectional view in Fig. 7, can only see more
One in a radial direction take over slot 76.In addition, annular intermediate cavity 74 is divided into the sub- intermediate cavity 75 of the imagination, the sub- intermediate cavity
Axially start in compensation opening 49, terminate on the second outer end 73 to overflow valve 41.
Fuel is made to be flowed out from lubricating cavity 40, also, by taking over by the gap flow channel 67 for being used as flow channel 43
Channel 70 makes fuel be supplied by being used as the take over channel 70 of flow channel 43 to fuel return line 34.Fuel return line 34
(being not shown in the figure 7) is fixed on the outer end of take over 68.Fuel is flowed by the communication port 79 of gap flow channel 67
In gap 61, also, it is flowed into overflow valve 41 from gap 61 by flow channel 48 when closure piston 46 is opened.Fuel from
First sub- cylinder space 57, which is flowed into intermediate cavity 74 and is flowed into from intermediate cavity 74 by above-mentioned two outflow opening 49, is used as
In the take over channel 70 of flow channel 43, so as to which the second outer end for making gap 61 also serves as flow channel 43.
Fuel return line 34 does not have stenosis and does not have dynamic head (Staudruck) in other words, so as in high-pressure pump 1
Make fuel return line 34 when shutdown and the shutdown of pre- delivery pump 35 and then take over channel 70 and intermediate cavity 74 flow air-fuel material, also
It is to say to be filled with air.When high-pressure pump 1 and pre- delivery pump 35 put into operation, pre- delivery pump 35 is such as divided into terms of transmission power
It puts so that closure piston 46 is slightly opened in normal operation, to ensure that the component inside lubricating cavity 40 is cooled.By
This, since closure piston 46 is as pre- delivery pump 35 puts into operation and opens, intermediate cavity 74 and then take over channel 70 are continuous
It is flowed through by fuel, so as to which volume of air that may be present in intermediate cavity 74 and take over channel 70 is full of by fuel at once, and
Thus air is emptied from intermediate cavity 74 in a short period of time after pre- delivery pump 35 and high-pressure pump 1 start.Spring cavity 58
(the second sub- cylinder space 58 in other words) is connected by compensating opening 49 with intermediate cavity 74 (or sub- intermediate cavity 75) in a manner of fluid communication
It connects.As a result, after pre- delivery pump 35 and high-pressure pump 1 start, the volume of air present in spring cavity 58 is open by compensating
59 can remove at once and rapidly and fill fuel, because since closure piston 46 moves back and forth and intermediate cavity 74 is by fuel
It fills and fuel is allow to be flowed into immediately in spring cavity 58 and it is possible thereby to makes spring cavity 58 in high-pressure pump 1 and pre- delivery pump
Fuel is filled in a short time after 35 startings.Due to making spring cavity 58 quick after being started in pre- delivery pump 35 and high-pressure pump 1
Fuel is filled, therefore can ensure thus closure piston 46 by fast cache, vibration motion does not occur so as to turn off piston 46.
As a whole, high-pressure pump 1 according to the invention has the advantages of notable.In order to reduce energy expenditure, fuel return pipe
Road does not have stenosis into without dynamic head.As a result, in the shutdown of high-pressure pump 1 and the shutdown of pre- delivery pump 35, air can
It enters in intermediate cavity 74 and also enters in spring cavity 51.After high-pressure pump 1 and pre- delivery pump 35 start, due to overflow
The size of valve 41, intermediate cavity 74 fill fuel, also, since intermediate cavity 74 and spring cavity 58 pass through benefit immediately within the short time
It connects, therefore spring cavity 58 can also fill fuel in a short time with repaying 59 fluid communications of opening, so as in closure piston 46
Place is not in vibration motion in a long time.
Claims (23)
1. a kind of high-pressure pump (1), for conveying fuel, which includes：
Housing (8),
At least one piston (5), for conveying fuel,
At least one cylinder (6), for supporting at least one piston (5),
The gap (61) in the housing (8) is constructed, for setting overflow valve (41),
The internal overflow valve (41) in the gap (61) is arranged on, with inlet opening (47) and at least one outflow opening
(49),
Wherein, the gap (61) has the first inner end (65) and the second outer end (66), and the overflow valve (41) includes：
Valve chest (45), with valve barrel (44),
Closure piston (46), the closure piston can be transported in the valve barrel (44) inside between closed position and open position
It is dynamic, so that the overflow valve (41) is closed in the closed position and the overflow valve (41) is beaten in the open position
It opens,
Inlet opening (47), internal for applying the fluid to cylinder space (56), which is surrounded by the valve barrel (44),
At least one outflow opening (49), the fluid for that will imported into the cylinder space (56) are discharged,
The elastic valve member (51) being connect with the closure piston (46), can be to the closure piston using the elasticity valve member
(46) apply pressure, the pressure reversal by the internal fluid of the cylinder space (56) in can be applied on the closure piston (46)
Pressure, so as to which the closure piston (46) by the elastic valve member (51) and by the fluid by means of being applied to the pass
The pressure closed on piston (46) and can be moved between the closed position and the open position,
Wherein, the valve chest (45) is upper on the outside does not have to be axially fixed on the high-pressure pump (1) housing (8)
Fixing device (38) in the gap (61),
It is characterized in that,
The high-pressure pump includes：
Have at least one cam (3) drive shaft (2) and
Lubricating cavity (40),
Wherein, at least one piston (5) is supported on indirectly in the drive shaft (2) at least one cam (3), from
And at least one piston (5) can implement translational motion due to the drive shaft (2) rotary motion, also,
The second outer end (66) of the gap (61) passes through the lubricating cavity (40) for fuel to be guided, also,
The cylinder space (56) is divided into the first sub- cylinder space (57) and the second sub- cylinder space (58) by the closure piston (46),
Also,
The inlet opening (47) and at least one outflow opening (49) are led in the described first sub- cylinder space (57), and
And
The elasticity valve member (51) is arranged on as the second of spring cavity (58) the sub- cylinder space (58) inside, also,
One compensation opening (59) is led to across the valve chest (45) in the described second sub- cylinder space (58).
2. high-pressure pump described in accordance with the claim 1, which is characterized in that the second outer end (66) of the gap (61) is as stream
Dynamic channel (43), fuel to be exported from the gap (61).
3. according to the high-pressure pump described in claims 1 or 2, which is characterized in that the valve chest (45) is upper on the outside not to have use
In the screw thread (60) being axially fixed on the high-pressure pump (1) housing (8) in the gap (61).
4. according to the high-pressure pump described in claims 1 or 2, which is characterized in that the compensation opening (59) extends radially through described
Valve chest (45).
5. according to the high-pressure pump described in claims 1 or 2, which is characterized in that the longitudinal axis (77) in the overflow valve (41)
On direction, only between the inlet opening (47) and at least one outflow opening (49), on the valve chest (45)
It is configured with and/or is provided with seal groove (62) and/or sealing ring (63).
6. according to the high-pressure pump described in claims 1 or 2, which is characterized in that a gap flow channel (67) leads to the gap
(61) in, also, on the direction of the longitudinal axis (77) of the gap (61), at least one stream with the overflow valve (41)
Go out opening (49) to compare, the inlet opening (47) of the overflow valve (41) is with the extremely gap flow channel (67) to the sky
The smaller spacing of communication port (79) and/or the gap (61) in gap (61) are configured to hole (64).
7. according to the high-pressure pump described in claims 1 or 2, which is characterized in that the high-pressure pump (1) housing (8) with it is described
Sealing ring (63) is configured between overflow valve (41).
8. according to the high-pressure pump described in claims 1 or 2, which is characterized in that in second outer end (66) of the gap (61)
Region in be equipped with and take over (68), this, which is taken over, has take over channel (70) inside the gap (61), also, it is described take over it is logical
Road (70) is for guiding fuel.
9. according to high-pressure pump according to any one of claims 8, which is characterized in that outer axial end portion (73) placement of the overflow valve (41)
It is taken on (68) described, and thus the overflow valve (41) is fixed in the axial direction in the gap (61).
10. according to high-pressure pump according to any one of claims 8, which is characterized in that borrowed inside the gap (61) take over (68)
Help press-fit connecting portion to connect with the housing (8) of the high-pressure pump (1).
11. according to the high-pressure pump described in claims 1 or 2, which is characterized in that on the axial direction of the overflow valve (41),
Between the outflow opening (49) of the overflow valve (41) and the outer axial end portion (73) of the overflow valve (41), in the valve casing
Be configured with intermediate cavity (74) between body (45) and the housing (8) of the high-pressure pump (1), for by fuel from the outflow opening
(49) it guides to the outer axial end portion (73) of the overflow valve (41).
12. according to the high-pressure pump described in claim 11, which is characterized in that the swept volume of the closure piston (46) is more than institute
State the volume of intermediate cavity (74).
13. according to the high-pressure pump described in claim 11, which is characterized in that the intermediate cavity (74) is divided into axial son
Between chamber (75), the sub- intermediate cavity be located at lead to as in second of spring cavity (58) sub- cylinder space (58) compensation be open (59)
Between the outer axial end portion (73) of the overflow valve (41), also, the swept volume of the closure piston (46) is more than described
The volume of sub- intermediate cavity (75).
14. according to the high-pressure pump described in claims 1 or 2, which is characterized in that inlet opening (47) structure of the overflow valve (41)
It makes on the interior axial end portion (72) of the overflow valve (41).
15. high-pressure pump described in accordance with the claim 1, which is characterized in that the fuel is diesel oil or gasoline.
16. high-pressure pump described in accordance with the claim 1, which is characterized in that the elasticity valve member (51) is valve spring (52).
17. according to the high-pressure pump described in claims 1 or 2, which is characterized in that the longitudinal axis (77) in the overflow valve (41)
On direction, only between the inlet opening (47) and at least one outflow opening (49), in the valve chest (45)
Seal groove (62) and/or sealing ring (63) are configured with and/or are provided on outside.
18. according to the high-pressure pump described in claim 7, which is characterized in that in the side of the longitudinal axis (77) of the gap (61)
Upwards, the sealing ring (63) orients between the inlet opening (47) and at least one outflow opening (49).
19. according to high-pressure pump according to any one of claims 8, which is characterized in that take over (68) are that reflux is taken over (69).
20. according to the high-pressure pump described in claim 11, which is characterized in that the intermediate cavity (74) is ring-shaped.
21. according to the high-pressure pump described in claims 1 or 2, which is characterized in that on the axial direction of the overflow valve (41),
Between the outflow opening (49) of the overflow valve (41) and the outer axial end portion (73) of the overflow valve (41), in the valve casing
Be configured with intermediate cavity (74) between body (45) and the housing (8) of the high-pressure pump (1), for by fuel from the outflow opening
(49) it guides to the second end (66) of the gap (61).
22. a kind of high-pressure injection system (36), for internal combustion engine (39), which includes：
High-pressure pump (1), with lubricating cavity (40) and overflow valve (41),
Pre- delivery pump (35),
High voltage rail (30),
It is characterized in that,
The high-pressure pump (1) is configured to according to the high-pressure pump described in any one of claim 1 to 21.
23. according to the high-pressure injection system (36) described in claim 22, which is characterized in that the high-pressure injection system (36) is
For the high-pressure injection system of the internal combustion engine (39) of motor vehicle.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE201310201892 DE102013201892A1 (en) | 2013-02-06 | 2013-02-06 | Valve |
| DE102013201892.4 | 2013-02-06 | ||
| PCT/EP2013/076667 WO2014121870A1 (en) | 2013-02-06 | 2013-12-16 | Valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104981605A CN104981605A (en) | 2015-10-14 |
| CN104981605B true CN104981605B (en) | 2018-06-08 |
Family
ID=49911493
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380072317.XA Active CN104981605B (en) | 2013-02-06 | 2013-12-16 | Valve |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2954192B1 (en) |
| CN (1) | CN104981605B (en) |
| DE (1) | DE102013201892A1 (en) |
| WO (1) | WO2014121870A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105464863A (en) * | 2015-12-09 | 2016-04-06 | 中国船舶重工集团公司第七一一研究所 | Electronic unit pump system and oil spray control method |
| GB201602013D0 (en) * | 2016-02-04 | 2016-03-23 | Delphi Internat Operations Luxembourg S À R L | High pressure diesel fuel pump |
| CN107762691A (en) * | 2017-09-19 | 2018-03-06 | 北汽福田汽车股份有限公司 | Pipe connecting component and vehicle |
| GB2570648B (en) * | 2018-01-26 | 2020-10-14 | Delphi Tech Ip Ltd | Fuel Pump |
| DE102019203967A1 (en) * | 2018-03-27 | 2019-10-02 | Keihin Corporation | VALVE UNIT FASTENING STRUCTURE AND FLUID PUMP WHICH USES SELF |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101849096A (en) * | 2007-11-05 | 2010-09-29 | 罗伯特·博世有限公司 | Fuel overflow valve for a fuel injection system, and fuel injection system having a fuel overflow valve |
| CN101868614A (en) * | 2007-11-23 | 2010-10-20 | 罗伯特·博世有限公司 | Safety valve and high-pressure pump comprising said safety valve |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4518140B2 (en) * | 2007-12-05 | 2010-08-04 | 株式会社デンソー | Fuel supply device |
| JP4968037B2 (en) * | 2007-12-13 | 2012-07-04 | 株式会社デンソー | Back pressure control valve and low pressure fuel system using the same |
| 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 |
| DE102009027146A1 (en) * | 2009-06-24 | 2010-12-30 | Robert Bosch Gmbh | Fuel high-pressure pump for fuel system of internal combustion engine, has suction side low pressure area, in which overflow valve is arranged, where overflow valve has valve housing with inlet, outlet, valve body and valve spring |
| ITMI20110582A1 (en) * | 2011-04-08 | 2012-10-09 | Bosch Gmbh Robert | PUMPING GROUP FOR FOOD FUEL, PREFERIBLY GASOIL, FROM A CONTAINMENT TANK TO AN INTERNAL COMBUSTION ENGINE |
| DE102012200894A1 (en) * | 2012-01-23 | 2013-07-25 | Robert Bosch Gmbh | High-pressure fuel pump of an injection system |
-
2013
- 2013-02-06 DE DE201310201892 patent/DE102013201892A1/en not_active Withdrawn
- 2013-12-16 CN CN201380072317.XA patent/CN104981605B/en active Active
- 2013-12-16 WO PCT/EP2013/076667 patent/WO2014121870A1/en active Application Filing
- 2013-12-16 EP EP13815445.5A patent/EP2954192B1/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101849096A (en) * | 2007-11-05 | 2010-09-29 | 罗伯特·博世有限公司 | Fuel overflow valve for a fuel injection system, and fuel injection system having a fuel overflow valve |
| CN101868614A (en) * | 2007-11-23 | 2010-10-20 | 罗伯特·博世有限公司 | Safety valve and high-pressure pump comprising said safety valve |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2014121870A1 (en) | 2014-08-14 |
| EP2954192A1 (en) | 2015-12-16 |
| DE102013201892A1 (en) | 2014-08-07 |
| EP2954192B1 (en) | 2017-10-25 |
| CN104981605A (en) | 2015-10-14 |
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