CN104981605A - Valve - Google Patents
Valve Download PDFInfo
- Publication number
- CN104981605A CN104981605A CN201380072317.XA CN201380072317A CN104981605A CN 104981605 A CN104981605 A CN 104981605A CN 201380072317 A CN201380072317 A CN 201380072317A CN 104981605 A CN104981605 A CN 104981605A
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- CN
- China
- Prior art keywords
- valve
- space
- service pump
- relief valve
- pressure service
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- 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
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- 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
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- 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
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- 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
Abstract
The invention provides a valve (42), in particular an overflow valve (41), for arrangement in a recess in a housing of a high pressure pump, said valve comprising a valve housing (45) that has a valve cylinder (44), a closing piston (46) movable within said valve cylinder (44) between a closed position and an open position such that in the closed position the valve (42) is closed and in the open position the valve (42) is open, an inlet opening (47) for supplying a fluid into the interior of a cylinder chamber (56) enclosed by the valve cylinder (44), at least one outlet opening (49) for discharging the fluid introduced into the cylinder chamber (56), an elastic valve element (51), in particular a valve spring (52), which is connected to the closing piston (46) and by means of which a compressive force can be applied to the closing piston (46), said compressive force being counter to a compressive force that can be applied to the closing piston (46) by the fluid within the cylinder chamber (56) such that the closing piston (46) can be moved, by means of the compressive force applied to the closing piston (46) by the elastic valve element (51) and the fluid, between the closed position and the open position, wherein said valve housing (45) does not have, on the outside, any fastening system, in particular not a thread or bayonet connection, for axial securing in the recess in the housing of the high pressure pump.
Description
Technical field
The present invention relates to a kind of according to claim 1 valve as described in the preamble, a kind of according to claim 4 high-pressure service pump as described in the preamble and one according to claim 15 high-pressure injection system as described in the preamble.
Background technique
In the high-pressure injection system of internal-combustion engine, particularly in the joint-track type ejecting system of diesel engine or petrol engine, the pressure maintained in the high pressure accumulator of joint-track type ejecting system is responsible for enduringly by high-pressure service pump.Such as, high-pressure service pump can be driven by means of live axle by the camshaft of internal-combustion engine.In order to by fuel area density to high-pressure service pump, employ pre-transfer pump (such as gear pump or rotary vane pump), these pre-transfer pumps are prepended to high-pressure service pump.Fuel is delivered to high-pressure service pump from fuel tank by fuel conduit by pre-transfer pump.
In addition, use reciprocating pump as high-pressure service pump.Be supported with live axle in the housing.Piston is radially arranged in cylinder relative to this live axle.The live axle being equipped with at least one cam is mounted with the roller of outfit roller-rolling surface, and this roller wheel bearing is in roller base.Roller base is connected with piston, thus makes piston positive become oscillating type translational motion.Spring pair roller seat applies the power be radially directed towards relative to live axle, thus roller is contacted with live axle all the time.Roller contacts using roller-rolling surface upper to be in live axle of axle-rolling surface (surface of live axle as having at least one cam).Roller is bearing in roller base by means of sliding supporting part.
Here, the live axle having described at least one cam, described roller and described roller base is arranged in the lubricating cavity of high-pressure service pump.The fuel being delivered to high-pressure service pump by pre-transfer pump is guided by this lubricating cavity, to lubricate the parts of this lubricating cavity inside on the one hand, and, these parts are cooled with the fuel flowing through lubricating cavity.Therefore, the fuel being delivered to high-pressure service pump by pre-transfer pump includes the fuel flowing through lubricating cavity on the one hand in volume flow, be positioned at the high-pressure service pump parts of lubricating cavity inside for lubrication and cooling, and further comprises the appointment fuel for high-pressure service pump, to be under high pressure delivered to high voltage rail.Here, from pre-transfer pump to the pressure substantial constant on the fuel conduit of high-pressure service pump.For this reason, to the flow channel of fuel tank, relief valve is being provided with to lubricating cavity or from lubricating cavity from pre-transfer pump.The space that relief valve is arranged on high-pressure service pump housing is inner.When higher than setting pressure (such as 5.5bar), relief valve is opened, and, thus many fuel is guided through lubricating cavity, and these fuel being guided through lubricating cavity are supplied to fuel tank again.When pressure before relief valve reduces, such as, time lower than 4.5bar, relief valve cuts out.
This relief valve has valve barrel and closure piston, and this closure piston is bearing in movingly on cylinder between closed position and open position.Fuel can be flow in relief valve by inlet opening and flow out from relief valve by flowing out opening.On the one hand, the fuel pressure at inlet opening place and a spring action are in closure piston.Here, to closure piston effect, to be placed in the power under pressure by spring and to be reciprocal by the fuel power be placed under pressure, thus when the fuel pressure at inlet opening place is different, closure piston is moved at cylinder interior.Here, the outflow opening leading to the cylinder space surrounded by cylinder is closed when closure piston is in the closed position.Only when the pressure at inlet opening place is improved by fuel, closure piston just moves in open position, in this open position, is not closed piston closes at the outflow opening at cylinder space place.
Cylinder space is closed piston and is divided into the first sub-cylinder space and the second sub-cylinder space as spring chamber.Spring is provided with in the second sub-cylinder space in other words spring chamber, and, compensate opening and lead in spring chamber through valve barrel.In normal operation, spring chamber is with filling fuels, and compensation opening is used for enabling closure piston to-and-fro motion, because the volume of spring chamber changes when closure piston to-and-fro motion.Here, compensating opening and make closure piston to-and-fro motion be buffered together with spring chamber, only can flow out by compensating opening because be closed the fuel that piston extrudes in spring chamber, when the smaller volume of spring chamber then conversely.In from high-pressure service pump (or lubricating cavity) to the fuel return line of fuel tank not or have in the fuel return line of small return pressure, spring chamber may be there is and empty or lubricating cavity inflation.Thus, after high-pressure service pump puts into operation again again, closure piston is in longer a period of time or the buffering that do not occur all the time because the fuel of spring chamber inside causes, and this may result in closure piston vibration and cause noise to generate thus and additional mechanical load or relief valve wearing and tearing.
DE 10 2,009 026 596 A1 gives a kind of for carrying the high-pressure service pump of fluid, particularly fuel, it includes live axle, at least one piston, at least one cylinder for supporting piston, wherein, at least one piston described is supported at least one cam described indirectly or directly, thus makes at least one piston can implement translational motion due to live axle rotary motion.
Summary of the invention
According to valve of the present invention, particularly relief valve, for being arranged in the space of high-pressure service pump housing, this valve comprises: the valve chest being equipped with valve barrel; At the closure piston can moved in valve barrel inside between closed position and open position, thus valve cuts out in a closed position and valve is opened in the open position; Inlet opening, for applying the fluid to the cylinder interior volume of being surrounded by valve barrel; At least one flows out opening, for the fluid expulsion that will import in input cylinder space; The elasticity valve member, the particularly valve spring that are connected with closure piston, utilize this valve spring can apply pressure to closure piston, this pressure reversal is in being come directed by applied pressure by the fluid of cylinder interior volume to closure piston, thus closure piston by means of by elasticity valve member and be applied to by fluid the pressure on closure piston and can move between closed position and open position, wherein, valve chest do not have on outside for axial restraint in the space at high-pressure service pump housing place fixing device, particularly not there is screw thread or not there is socket connection.On valve chest, outside is not configured with for axial restraint in the space at high-pressure service pump housing place fixing device, be not particularly configured with screw thread or be not configured with outside thread.Thus, the intermediate cavity between valve chest and high-pressure service pump housing is flow through by fluid in the axial direction.Here, valve is axially fixed in inside, housing space generally to realize in the following manner: by the arrangement on the first inner end of valve and/or the second outer end; And/or by the arrangement of the seal ring on the seal groove on valve; And/or by the arrangement on the groove (particularly seal groove) on outside valve chest, wherein, the housing being placed in high-pressure service pump of described valve or valve chest realizes.In contrast to this, valve chest also can be configured with annular protrusion on outside, for by valve shaft to arrangement and be fixed on high-pressure service pump housing.
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 space, and, described inlet opening and at least one outflow opening described lead in the first sub-cylinder space, and, elasticity valve member is arranged on the second sub-cylinder interior volume as spring chamber, and compensates opening and particularly lead in the second sub-cylinder space radially across valve chest.
In a supplementary flexible program, on the longitudinal axis direction of valve, only flow out between opening at inlet opening and at least one, at valve chest place, (particularly on outside) is configured with and/or is provided with seal groove and/or seal ring.In addition, valve flows out between opening at inlet opening and at least one, therefore valve can when being arranged in housing space on outside by fluid winding flow.
According to the high-pressure service pump for transfer the fuel (such as diesel oil or gasoline) of the present invention, comprising: housing; Be equipped with the live axle of at least one cam; At least one piston, for transfer the fuel; At least one cylinder, for supporting at least one piston; Here, at least one piston is supported on indirectly to be had on the live axle of at least one cam, thus makes at least one piston can carry out translational motion due to the rotary motion of live axle; Lubricating cavity; Be configured in the space of enclosure interior, for arranging relief valve; Be arranged on the relief valve of inside, space, it has inlet opening and at least one flows out opening, and wherein, space has the first inner end and the second outer end, second outer end in space is used for fuel to be guided through lubricating cavity as flow channel, and is preferred for fuel to derive from space.Therefore, fuel can be guided by outer end, space second, thus also make the second outer end direction of the intermediate cavity between valve chest and high-pressure service pump housing towards relief valve from least one flows out opening be flow through by fuel thus in an advantageous manner, further, on the second outer end, by the air in this intermediate cavity, by importing fuel, by means of being guided through by fuel, intermediate cavity is next to be removed especially simply thus.
In a supplementary form of implementation, one space flow channel leads in space, and, on longitudinal axis direction, space, compared with flowing out opening with at least one of relief valve, the inlet opening of relief valve has less spacing to the communication port that space flow channel leads in space, and/or pore structure is hole.Fuel can be imported in space by space flow channel, and, until this section of the inlet opening of relief valve from first inner end in space, fuel is imported in the inlet opening of relief valve through space from space flow channel.
Desirably, between high-pressure service pump housing and relief valve, be configured with seal ring, and preferably, seal ring flows out between opening at inlet opening and at least one on the longitudinal axis direction in space and carries out orientation.Space is divided into by seal ring: the first sub-space, from space first inner end until seal ring; Second sub-space, from seal ring until outer end, space second.Here, the first and second sub-spaces fluidly seal so that seal ring is anti-, and, fuel can be made to guide to the second sub-space from the first sub-space by means of only opening relief valve.
In an additional flexible program, in the region of second outer end in space, be provided with adapter, particularly reflux adapter, it has the adapter passage in inside, space, and adapter passage is for guiding fuel.
In a supplementary configuration, the outer axial end portion of relief valve is placed in adapter, thus makes relief valve be fixed in the axial direction in space thus.Second outer end of relief valve (particularly valve chest) is placed in adapter, thus relief valve can be made thus to be fixed in the axial direction in space.Here desirably, relief valve is additionally placed on the housing of high-pressure service pump with seal ring in the axial direction, thus valve can be made thus to be fixed on the housing of high-pressure service pump on above-mentioned two axial directions.
In a supplementary configuration, take over and be connected with the housing of high-pressure service pump by means of press fit joint in inside, space.Adapter special mechanical type simply and reliably on high-pressure service pump housing can be made to be fixed on inside, space by means of press fit joint, and, also additionally can prevent the second outer end fluidly closing this space thus, thus only make fuel from space out by adapter passage on second outer end in space.
In a supplementary flexible program, the relief valve of high-pressure service pump is configured to relief valve illustrated in this protection application.
Desirably, on the axial direction of relief valve, between the outflow opening and the outer axial end portion of relief valve of relief valve, (particularly annular) intermediate cavity is configured with, for fuel is guided to the outer axial end portion of relief valve from flowing out opening and preferably to guide to the second end in space between valve chest and the housing of high-pressure service pump.When closure piston is opened, fuel can be flow in the first sub-cylinder space by the inlet opening of valve and flow out opening from the first sub-cylinder space by least one and flow into intermediate cavity.And then, from at least one flow out opening fuel out on outside axially (that is, on the longitudinal axis direction of valve) stream the relief valve between valve chest and high-pressure service pump housing from the first inner end of relief valve to the second outer end of relief valve.
In an additional form of implementation, the swept volume of valve piston is greater than the volume of intermediate cavity.The swept volume of valve piston is the volume in the first and/or second sub-cylinder space, this volume extruding closure piston between an open position and a closed.
In a supplementary flexible program, intermediate cavity is divided into leading to as the sub-intermediate cavity of axis between the compensation opening in second sub-cylinder space of spring chamber and the outer axial end portion of relief valve, further, the swept volume of valve piston is greater than the volume of sub-intermediate cavity.Compensation opening on valve chest from the second sub-cylinder space in other words spring chamber lead to the intermediate cavity between valve chest and high-pressure service pump housing.Therefore, for the air in sub-intermediate cavity, whole sub-intermediate cavity filled with fuel can be made by closure piston to-and-fro motion in other words of moving between an open position and a closed.Thus, if make when high-pressure service pump turns off sub-intermediate cavity at least in part (particularly fully) be full of air, just can especially safely and reliably with the sub-intermediate cavity of filling fuels.Therefore, when high-pressure service pump puts into operation again, sub-intermediate cavity (particularly intermediate cavity) also can filled with fuel again especially simply, thus closure piston can not be caused thus to vibrate, because spring chamber can be special simply and reliably by compensating opening filled with fuel again thus in other words in the second sub-cylinder space.
In a supplementary flexible program, the inlet opening of relief valve is configured on the interior axial end portion of relief valve.
According to of the present invention for internal-combustion engine, high-pressure injection system especially for Motor Vehicle, include: the high-pressure service pump with lubricating cavity and relief valve; Pre-transfer pump; High voltage rail; Wherein, relief valve is configured to illustrated relief valve and/or high-pressure service pump in this protection application and is configured to high-pressure service pump illustrated in this protection application.
In a supplementary form of implementation, in valve barrel, be provided with spring retainer, and this spring retainer is connected with elasticity valve member.
Preferably, elasticity valve member is arranged in cylinder space.
Desirably, at least one flow out opening be closed in the closed position of closure piston piston closes and/or at least one flow out opening lead in the open position of closure piston in the first sub-cylinder space.
In another form of implementation, compensate opening and lead in the second sub-cylinder space, for fluid being imported and deriving the second sub-cylinder space.Compensate opening to be used for fuel being imported and deriving the second sub-cylinder space.When closure piston moves, the volume in the second sub-cylinder space changes.In order to mainly make closure piston move, it is required that also fluid can be imported and derive the second cylinder space by the compensation opening with very small flow cross section in the incompressible situation of fuel.Here, also pressure surge may be caused at inlet opening place.The pressure surge of this particularly short time may cause vibration or the oscillating movement of closure piston.When compensating opening and there is reduced size and (particularly filling completely) being filled with liquid (particularly fuel) in the second sub-cylinder space, this concussion in other words faster reciprocal motion of closure piston caused by pressure surge can be reacted on thus, and, only because the pressure that the liquid on inlet opening is lasting changes, closure piston motion is just carried out at a slow speed on buffering ground, thus when the second sub-cylinder space fills liquid (particularly fuel), there will not be closure piston to vibrate and generate and mechanical wear with the noise caused thus.
In a supplementary flexible program, at least one flows out opening and leads to the second sub-cylinder space, particularly leads to the whole position of closure piston.
In another configuration, valve comprises at least in part, particularly fully by metal, such as steel or aluminium and/or be made of plastics.Metal is durable for the manufacture of valve and lasting material.Plastics have lighter weight in an advantageous manner, thus make the very light in weight of valve thus.Here, the plastics of glass fiber reinforcement are preferably related to when plastics.Preferably, valve chest and/or closure piston and/or spring retainer are fully made of plastics valve barrel at least in part, particularly in other words.
In a supplementary scheme, the volume of fuel stream being delivered to high-pressure service pump from pre-transfer pump can control and/or adjustable during internal combustion engine operation, its mode is, control and/or regulate the transmission power of this pre-transfer pump, or, utilize batching unit to control and/or regulate the flow cross section of the flow channel from pre-transfer pump to high-pressure service pump.If pre-transfer pump can control or adjustable in transmission power, then do not need batching unit, and the volume of fuel guiding to high-pressure service pump fluently controls with pre-transfer pump and/or regulates.If pre-transfer pump is uncontrollable and/or unadjustable in transmission power, then this utilizes batching unit to implement.
In another configuration, pre-transfer pump comprises motor.
Specifically, pre-conveying pump motor is integrated in pre-transfer pump, and permanent magnet such as, is encased in gear by its mode.
The pressure that can be produced in high voltage rail by high-pressure service pump, such as, for diesel engine, is in 1000bar to 3000bar scope, or, such as, for petrol engine, be between 40bar to 400bar.
Accompanying drawing explanation
Embodiments of the invention are illustrated below according to affiliated accompanying drawing.Shown in accompanying drawing:
Fig. 1: for carrying the high-pressure service pump drawing in side sectional elevation of fluid,
Fig. 2: there is the roller of roller base and the A-A sectional drawing according to Fig. 1 of live axle,
Fig. 3: the strong schematic representation of high-pressure injection system,
Fig. 4: the drawing in side sectional elevation with the strong simplification of the high-pressure service pump of pre-transfer pump,
Fig. 5: by the sectional arrangement drawing of the known relief valve of prior art,
Fig. 6: according to the sectional arrangement drawing of relief valve of the present invention,
Fig. 7: the sectional arrangement drawing of high-pressure service pump housing, this high-pressure service pump housing has according to relief valve of the present invention in housing space.
Embodiment
Figure 1 illustrates the drawing in side sectional elevation of the high-pressure service pump 1 for transfer the fuel.High-pressure service pump 1 is for being under high pressure delivered to internal-combustion engine 39 by fuel (such as gasoline or diesel oil).The pressure that can be produced by high-pressure service pump 1 to be such as between 1000bar to 3000bar in scope.
High-pressure service pump 1 has the live axle 2 of outfit two cams 3, and this live axle implements rotary motion around spin axis 26.Spin axis 26 be positioned at Fig. 1 plan and perpendicular to the plan of Fig. 2.Piston 5 is bearing in cylinder 6, and this cylinder is formed by housing 8.Active chamber 29 is by cylinder 6, housing 8 and piston 5 gauge.There is the inlet passage 22 entering valve 19 lead in active chamber 29 with the releasing passage 24 with bleeder 20.Fuel is flow in active chamber 29 by the opening that enters on inlet passage 22, and the fuel be under high pressure is flowed out from active chamber 29 again by the releasing opening 23 of releasing on passage 24.Enter valve 19 (such as safety check) to form as follows: fuel only can flow in active chamber 29, and bleeder 20 (such as safety check) is formed as follows: fuel only can flow out from active chamber 29.Due to the to-and-fro motion of piston 5 oscillating type, the volume-variation of active chamber 29.Piston 5 supports on driving shaft 2 indirectly.The end of piston 5 (in other words pump piston 5) is fixed with the roller base 9 being equipped with roller 10.Here, roller 10 can implement rotary motion, and the spin axis 25 of this roller is positioned at plan according to Fig. 1 and perpendicular to the plan of Fig. 2.The live axle 2 being equipped with at least one cam 3 has axle-rolling surface 4, and roller 10 has roller-rolling surface 11.
Roller-the rolling surface 11 of roller 10 has above-mentioned two cams 3 on surface of contact 12 axle-rolling surface 4 at live axle 2 rolls.Roller base 9 be bearing in by housing 8 form as in the roller base support of sliding supporting part.Clamp between housing 8 and roller base 9, as elastic component 28 spring 27 in other words helical spring 27 pressure is applied in roller base 9, thus the roller-rolling surface 11 of roller 10 contacts with the axle-rolling surface 4 of live axle 2 all the time.Therefore, roller base 9 and the to-and-fro motion of piston 5 common implementing oscillating type.Roller 10 is bearing in roller base 9 together with sliding supporting part 13.
Show the high-pressure injection system 36 for not shown Motor Vehicle with strong schematic diagram in figure 3, it has high voltage rail 30 or fuel rail 31.Fuel is injected in the firing chamber (not shown) of internal-combustion engine 39 from high voltage rail 30 or fuel rail 31 by means of valve (not shown).Fuel is delivered to high-pressure service pump 1 from fuel tank 32 by fuel conduit 33 by electronic pre-transfer pump 35.Here, high-pressure service pump 1 driven shaft 2 drives, and live axle 2 is axles (such as bent axle or camshaft) of internal-combustion engine 39.Batching unit 37 controls and/or regulates time per unit to guide to the volume of fuel of high-pressure service pump 1.High voltage rail 30 is for being injected to fuel in the firing chamber of internal-combustion engine 39.Here, the unwanted fuel of high-pressure service pump 1 is led back to again in fuel tank 32 by optional fuel return line 34.
Fig. 4 shows a part for high-pressure injection system 36.Lubricating cavity 40 is had in housing 8 internal structure of high-pressure service pump 1.Live axle 2, roller 10, roller base 9 (not shown in the diagram) and be partly provided with piston 5 is provided with in lubricating cavity 40.By fuel is directed through lubricating cavity 40, make these parts 2,5,9 and 10 fuel lubricated.For this reason, be provided with flow channel 43 in housing 8 inside, and fuel to be flow in lubricating cavity 40 by this flow channel 43 and flows out from this lubricating cavity again subsequently, further, after flowing out from lubricating cavity 40, fuel tank 32 (Fig. 4) is supplied to again by fuel return line 34.Show in detail the high-pressure injection system 36 shown in Fig. 3 in the diagram, and high pressure-rail 30 and internal-combustion engine 39 are not shown.Here, with the embodiment shown in Fig. 3 unlike, the high-pressure injection system 36 in specific embodiment shown in Figure 4 does not have batching unit 37.In embodiment shown in Figure 4, pre-transfer pump 35 can control and/or adjustable in transmission power, and this pre-transfer pump is driven by motor 17.Pre-transfer pump 35 is configured to gear pump 14 (such as internal gear pump 15 or external gear pump 16) and illustrates simplifiedly by force.High-pressure service pump 1 (what that is, be supplied to high-pressure service pump 1 enters valve 22) is supplied to by the pre-transfer pump 35 with pre-discharge pressure (such as 4bar) by fuel conduit 33 by the fuel that pre-transfer pump 35 aspirates from fuel tank 32.In addition, at the run duration of internal-combustion engine 39, the fuel carried by pre-transfer pump 35 is flowed out from lubricating cavity 40, to lubricate such as live axle 2, roller 10 and piston 5 by relief valve 41 and the flow channel 43 being placed on relief valve 41 after flowing through lubricating cavity 40.In flow in fuel after lubricating cavity 40, fuel is supplied to fuel tank 32 by flow channel 43 and fuel return line 34 again.Thus, these parts 2,5,9 and 10 can lubricated and also can be cooled.Here, relief valve 41 is formed as follows, there is constant pressure (that is the pre-discharge pressure of 4.5bar) in the fuel conduit 43 before relief valve 41 and in the fuel conduit 43 leading in lubricating cavity 40.Here, except the fuel delivery for high-pressure service pump 1, the amount of extra fuel for lubricating this high-pressure service pump 1 (that is, flowing through the fuel of lubricating cavity 40) also carried by pre-transfer pump 35.In order to avoid the pressure at fuel conduit 33 place when pre-transfer pump 35 improves transmission power before relief valve 41 raises, when the fuel pressure before relief valve 41 raises (such as from 5.5bar pressure), relief valve 41 is additionally opened, that is, provide fuel through the larger flow cross-section of relief valve 41, till the pressure before relief valve is 4.5bar again.When pressure in fuel conduit 33 before relief valve 41 is less than 4.5bar, relief valve 41 cuts out.Thus, at internal-combustion engine 39 run duration, the pre-discharge pressure of substantial constant between 4.5bar to 5.5bar can be provided, even if be also like this when the transmission power of pre-transfer pump 35 fluctuates a little with reference to the volume flow needed for high-pressure service pump 1 in fuel conduit 33 before relief valve 41.
Figure 5 illustrates the relief valve 41 of valve 42 well known in the prior art as high-pressure injection system 36.Relief valve 41 has valve chest 45, and this valve chest is to valve barrel 44 gauge.The outside of valve chest 45 is configured with screw thread 60 as outside thread 60, this screw thread forms fixing device 38, inner for being axially fixed in space 61 on the housing 8 of high-pressure service pump 1.Closure piston (Schlie β kolben) 46 is had at valve barrel 44 interior support.Due to the sliding supporting part on valve barrel 44, closure piston 46 can implement axial motion, that is according to Fig. 6 diagram from left to right and vice versa.Valve barrel 44 or valve chest 45 enclose cylinder space 56.Here, cylinder space 56 is closed piston 46 and is divided into the first sub-cylinder space 57 and the second sub-cylinder space 58.Inlet opening 47 for fluid (particularly fuel) leads in the first sub-cylinder space 57, because be processed with flow channel 48 in valve chest 45.Here, flow channel 48 is configured in valve chest 45 in the axial direction.In addition, two flow out openings 49 and lead in the first sub-cylinder space 57, because be processed with two radial flow pass 50 in valve chest 45.Closure piston 46 (in other words half sphere shape 46) in the axial section with larger diameter or radius by means of sliding supporting part to be bearing on valve barrel 44.On the second section, closure piston 46 has less diameter, and in this region, section right part with small diameter, closure piston 46 has sealing seat 54.
Valve spring 52 is provided with as elasticity valve member 51 in the second sub-cylinder space 58.Here, elasticity valve member 51 is fixed at one end on fastening spring retainer 53, is fixed on an opposite end on closure piston 46.Spring retainer 53 encloses valve barrel 44 and is configured to independent component and is complemented at valve chest 45.This unlike, spring retainer 53 also integrally can form (not shown) with valve chest 45.On outside, valve chest 45 is configured with two seal grooves 62, in these grooves, is respectively equipped with seal ring 63 (such as elastic caoutchouc Sealing).Thus, valve chest 45 can be integrated or be encased in the housing 8 of high-pressure service pump by means of seal ring 63.For this reason, the housing 8 of high-pressure service pump 1 has the hole 64 that respective complementary constructs or the opening had as space 61, and seal ring 63 is placed on this hole or opening, and makes flow channel 43 can be directed across flow channel 48 and above-mentioned two flow pass 50 thus.
Figure 5 illustrates the outs open position of closure piston 46.In this outs open position, above-mentioned two flow out opening 49 parts and are closed piston 46 and have larger-diameter section and close, and part can make fluid flow out openings 49 by above-mentioned two to flow out from the first sub-cylinder space 57.Here, fluid (particularly fuel) is flow in the first sub-cylinder space 57 by flow channel 48.If the fuel pressure in the first sub-cylinder space 57 continues to improve (being such as increased to exceed the value of 5bar), then make due to the larger reason of the fuel pressure in the first sub-cylinder space 57 closure piston 46 continue to left movement against by valve spring 52 applied pressures, thus therefore make above-mentioned two flow pass 50 continue to open.When falling under stress, closure piston 46 moves right so far away, till sealing seat 54 encloses inlet passage 48 (enclosing the inlet opening 47 led in the first sub-cylinder space 57 in other words) completely.Between closure piston 46 moving period, the volume in the second sub-cylinder space 58 also changes.Have between larger-diameter section and valve barrel 44 at closure piston 46 and have small gap, thus in very small region, make fuel also arrive the second sub-cylinder space 58 from the first sub-cylinder space 57.Therefore, as long as the second sub-cylinder space 58 (in other words spring chamber 58) is not full of air, then therefore the second sub-cylinder space 58 is filled with incompressible fuel substantially due to the slight pressure in fuel return line 34.In order to closure piston 46 mainly can be made to move, then it is required that the fuel be in the second sub-cylinder space 58 can outwards flow out and flow into again from the second sub-cylinder space 58 by compensating opening 59.Here, compensate opening 59 and there is very little diameter or little flow cross section (such as diameter be between 0.5mm to 1mm in scope).Thus, the pressure surge of the fuel in inlet opening 47 region can not cause closure piston 46 to vibrate, because make fuel only flow into lentamente by compensating opening 59 and flow out the second sub-cylinder space 58, when the fuel thus only in inlet opening 47 region is in the change of suitable chronic stress, closure piston 46 kicking motion just can be caused.Sealing seat 54 can seal relief valve 41 completely in an advantageous manner in the closed position of closure piston 46.
Figure 6 illustrates the sectional arrangement drawing according to relief valve 41 of the present invention.Substantially the difference with the relief valve 41 of the prior art shown in Fig. 5 is only described below.Valve chest 45 does not have screw thread as the fixing device for being axially fixed in by valve chest 45 on high-pressure service pump 1 housing 8 on outside.Therefore, axially, that is (Fig. 7) on the housing 8 of high-pressure service pump can not be fixed in the axial direction along the longitudinal axis 77 of valve 42 or the direction of longitudinal axis 77 in the space 61 that is configured to hole 64 according to relief valve 41 of the present invention.In order to by relief valve 41 axial restraint, the seal ring 63 on the seal groove 62 of valve chest 45 is placed on the flange 78 of high-pressure service pump 1 housing 8.Valve 42 has the first inner end 72 and the second outer end 73.Second outer end 73 of relief valve 41 is mounted with the adapter 68 being configured to backflow adapter 69.Adapter 68 by means of press fit joint (Pressverbund) 71 and the housing 8 of high-pressure service pump 1 realize Fluid Sealing ground and force closure be connected.
As already mentioned, in the housing 8 of high-pressure service pump 1, be processed with the space 61 being configured to hole 64, this space has longitudinal axis 77.Hole 64 has the first inner end 65 and the second outer end 66.Due on the end that the second outer end 73 of relief valve 41 is placed in adapter 68 and seal ring 63 is placed on the flange 78 of housing 8, to be therefore fixed on hole 64 in the axial direction inner for valve 42.Only flow out between openings 49 and inlet opening 47 at above-mentioned two according to relief valve 41 of the present invention, on the first inner end 72 of relief valve 41, there is seal ring 63, thus therefore enable the intermediate cavity 74 in axis 77 direction along the longitudinal (from above-mentioned two flow out openings 49 or from seal ring 63 until the second outer end 73 of relief valve 41) flowed out from above-mentioned two the fuel that openings 49 flow out when closure piston 46 is opened and flow through.On the end of adapter 68 being arranged at inside, hole 64, be configured with multiple radial adapter groove 76, thus enable the fuel flowing through intermediate cavity 74 flow to adapter passage 70 in radial directions by these radial adapter grooves 76 in the region of the second outer end 73 of relief valve 41.Due to the sectional drawing in Fig. 7, in multiple radial adapter groove 76 can only be seen.In addition, annular intermediate cavity 74 is divided into the sub-intermediate cavity 75 of the imagination, and described sub-intermediate cavity axially starts, terminates to the second outer end 73 of relief valve 41 on compensation opening 49.
By making fuel flow out from lubricating cavity 40 as the space flow channel 67 of flow channel 43, and, make fuel pass through to be supplied to fuel return line 34 as the adapter passage 70 of flow channel 43 by adapter passage 70.Fuel return line 34 (not shown in the figure 7) is fixed on the outer end of adapter 68.Fuel is flow in space 61 by the communication port 79 of space flow channel 67, and, flow into relief valve 41 by flow channel 48 from space 61 when closure piston 46 is opened.Fuel flows out openings 49 from the first sub-cylinder space 57 by above-mentioned two and to flow in intermediate cavity 74 and to flow in the adapter passage 70 as flow channel 43 from intermediate cavity 74, thus makes second outer end in space 61 also be used as flow channel 43.
Fuel return line 34 does not have stenosis and does not have dynamic head (Staudruck) in other words, thus make fuel return line 34 and then adapter passage 70 and intermediate cavity 74 flow empty fuel when high-pressure service pump 1 turns off and pre-transfer pump 35 turns off, be that is filled with air.When high-pressure service pump 1 and pre-transfer pump 35 put into operation, pre-transfer pump 35 is arranged as follows in transmission power, and closure piston 46 in normal operation is opened a little, to ensure that the parts in lubricating cavity 40 inside are cooled.Thus, open because closure piston 46 puts into operation along with pre-transfer pump 35, therefore intermediate cavity 74 and then adapter passage 70 are constantly flow through by fuel, thus the volume of air that may exist in intermediate cavity 74 and adapter passage 70 is full of by fuel at once, and in a short period of time air is emptied from intermediate cavity 74 after pre-transfer pump 35 and high-pressure service pump 1 start thus.Spring chamber 58 (in other words the second sub-cylinder space 58) is connected in the mode of fluid communication with intermediate cavity 74 (or sub-intermediate cavity 75) to compensate opening 49.Thus, after pre-transfer pump 35 and high-pressure service pump 1 start, the volume of air existed in spring chamber 58 can be removed and filled with fuel by compensating opening 59 at once and rapidly because due to closure piston 46 to-and-fro motion and intermediate cavity 74 made by filling fuels fuel can flow into immediately in spring chamber 58 and spring chamber 58 filled with fuel at short notice after high-pressure service pump 1 and pre-transfer pump 35 start can be made thus.After starting at pre-transfer pump 35 and high-pressure service pump 1, make spring chamber 58 filled with fuel fast, therefore can ensure that closure piston 46 is by fast cache, thus make closure piston 46 not occur oscillating movement thus.
As a whole, significant advantage is had according to high-pressure service pump 1 of the present invention.In order to reduce energy ezpenditure, fuel return line does not have stenosis and then does not have dynamic head.Thus, when high-pressure service pump 1 turns off and pre-transfer pump 35 turns off, air can enter into intermediate cavity 74 and also enter into spring chamber 51.After high-pressure service pump 1 and pre-transfer pump 35 start, due to the size of relief valve 41, intermediate cavity 74 filled with fuel immediately within the short time, and, because intermediate cavity 74 and spring chamber 58 by being connected with compensating opening 59 fluid communication, therefore spring chamber 58 also can filled with fuel at short notice, thus closure piston 46 be in long-time in there will not be oscillating movement.
Claims (15)
1. a valve (42), particularly relief valve (41), for being arranged in the space (61) of the housing (8) of high-pressure service pump (1), this valve comprises:
-valve chest (45), it has valve barrel (44),
-closure piston (46), this closure piston can move between closed position and open position in described valve barrel (44) inside, thus described valve (42) is cut out in described closed position and described valve (42) is opened in described open position
-inlet opening (47), inner for applying the fluid to cylinder space (56), this cylinder space is surrounded by described valve barrel (44),
-at least one outflow opening (49), for the fluid expulsion in described cylinder space (56) will be imported to,
-elasticity the valve member (51), the particularly valve spring (52) that are connected with described closure piston (46), utilize this valve spring can apply pressure to described closure piston (46), this pressure reversal is in can be applied to the pressure on described closure piston (46) by the fluid that described cylinder space (56) is inner, thus described closure piston (46) is by means of by described elasticity valve member (51) and be applied to the pressure on described closure piston (46) by described fluid and can move between described closed position and described open position
It is characterized in that, described valve chest (45) does not have for being axially fixed on fixing device (38) in described space (61) on described high-pressure service pump (1) housing (8), particularly not having screw thread (60) on outside.
2. according to valve according to claim 1, it is characterized in that, described cylinder space (56) is divided into the first sub-cylinder space (57) and the second sub-cylinder space (58) by described closure piston (46), and, described inlet opening (47) and at least one outflow opening (49) described are led in described first sub-cylinder space (57), and, the second sub-cylinder space (58) that described elasticity valve member (51) is arranged on as spring chamber (58) is inner, and, compensate opening (59) to pass, particularly extend radially through described valve chest (45) to lead in described second sub-cylinder space (58).
3. according to the valve described in claim 1 or 2, it is characterized in that, on longitudinal axis (77) direction of described valve (42), only described inlet opening (47) and described at least one flow out between opening (49), upper at described valve chest (45), particularly on outside, be configured with and/or be provided with seal groove (62) and/or seal ring (63).
4. a high-pressure service pump (1), for transfer the fuel, such as diesel oil or gasoline, this high-pressure service pump includes:
-housing (8),
-live axle (2), it has at least one cam (3),
-at least one piston (5), for transfer the fuel,
-at least one cylinder (6), for supporting described at least one piston (5),
-wherein, described at least one piston (5) be indirectly supported on there is described at least one cam (3) live axle (2) on, thus described at least one piston (5) can implement translational motion due to (2) rotary motion of described live axle
-lubricating cavity (40),
-be configured in space (61) in described housing (8), for arranging relief valve (41),
-being arranged on the inner relief valve (41) in described space (61), it has inlet opening (47) and at least one flows out opening (49),
It is characterized in that, described space (61) has the first inner end (65) and the second outer end (66), and, second outer end (66) in described space (61) is for making fuel by described lubricating cavity (40), further, this second outer end is preferably provided with flow channel (43) for being derived from described space (61) by fuel.
5. according to high-pressure service pump according to claim 4, it is characterized in that, one space flow channel (67) leads in described space (61), and, on the direction of the longitudinal axis (77) of described space (61), compared with flowing out opening (49) with at least one of described relief valve (41), the inlet opening (47) of described relief valve (41) has the spacing less to the communication port (79) in described space (61) to described space flow channel (67), and/or described space (61) are configured to hole (64).
6. according to the high-pressure service pump described in claim 4 or 5, it is characterized in that, seal ring (63) is configured with between the housing (8) and described relief valve (41) of described high-pressure service pump (1), and, on the direction of the longitudinal axis (77) of described space (61), preferred described seal ring (63) described inlet opening (47) and described at least one to flow out between opening (49) directed.
7. according to the one or more described high-pressure service pump in claim 4 to 6, it is characterized in that, in the region of second outer end (66) of described space (61), be provided with adapter (68), particularly reflux adapter (69), this adapter has adapter passage (70) in described space (61) inside, further, described adapter passage (70) is for guiding fuel.
8. according to high-pressure service pump according to claim 7, it is characterized in that, the outer axial end portion (73) of described relief valve (41) is placed in described adapter (68), thus described relief valve (41) is fixed in described space (61) in the axial direction thus.
9. according to the high-pressure service pump described in claim 7 or 8, it is characterized in that, described adapter (68) is connected with the housing (8) of described high-pressure service pump (1) by means of press fit joint in described space (61) inside.
10., according to the one or more described high-pressure service pump in claim 4 to 9, it is characterized in that, described relief valve (41) is according to the one or more structure in claims 1 to 3.
11. according to the one or more described high-pressure service pump in claim 4 to 10, it is characterized in that, on the axial direction of described relief valve (41), between the outflow opening (49) and the outer axial end portion (73) of described relief valve (41) of described relief valve (41), the intermediate cavity (74) of particularly annular is configured with between described valve chest (45) and the housing (8) of described high-pressure service pump (1), for fuel to be guided to the outer axial end portion (73) of described relief valve (41) from described outflow opening (49), and preferably guide to the second end (66) of described space (61).
12., according to high-pressure service pump according to claim 11, is characterized in that, the swept volume of described valve piston (46) is greater than the volume of described intermediate cavity (74).
13. according to the high-pressure service pump described in claim 11 or 12, it is characterized in that, described intermediate cavity (74) is divided into axial sub-intermediate cavity (75), this sub-intermediate cavity is arranged in leads to as between the compensation opening (59) of second sub-cylinder space (58) of spring chamber (58) and the outer axial end portion (73) of described relief valve (41), further, the swept volume of described valve piston (46) is greater than the volume of described sub-intermediate cavity (75).
14. according to the one or more described high-pressure service pump in claim 4 to 13, it is characterized in that, the inlet opening (47) of described relief valve (41) is configured on the interior axial end portion (72) of described relief valve (41).
15. 1 kinds of high-pressure injection systems (36), for internal-combustion engine (39), especially for Motor Vehicle, this high-pressure injection system includes:
-high-pressure service pump (1), it has lubricating cavity (40) and relief valve (41),
-pre-transfer pump (35),
-high voltage rail (30),
It is characterized in that,
Described relief valve (41) constructs according to one or more described in claims 1 to 3, and/or
Described high-pressure service pump (1) constructs according to one or more described in claim 4 to 14.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013201892.4 | 2013-02-06 | ||
| DE201310201892 DE102013201892A1 (en) | 2013-02-06 | 2013-02-06 | Valve |
| PCT/EP2013/076667 WO2014121870A1 (en) | 2013-02-06 | 2013-12-16 | Valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104981605A true CN104981605A (en) | 2015-10-14 |
| CN104981605B 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) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN111656001A (en) * | 2018-01-26 | 2020-09-11 | 德尔福知识产权有限公司 | Fuel pump |
Families Citing this family (3)
| 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 |
| DE102019203967A1 (en) * | 2018-03-27 | 2019-10-02 | Keihin Corporation | VALVE UNIT FASTENING STRUCTURE AND FLUID PUMP WHICH USES SELF |
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| US20090145403A1 (en) * | 2007-12-05 | 2009-06-11 | Denso Corporation | Fuel supply system having fuel filter installed downstream of feed pump |
| US20090151700A1 (en) * | 2007-12-13 | 2009-06-18 | Denso Corporation | Backpressure valve and fuel system having the same |
| 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 |
| WO2012136429A1 (en) * | 2011-04-08 | 2012-10-11 | Robert Bosch Gmbh | Pump unit for supplying fuel, preferably diesel oil, from a containing tank to an internal combustion engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| 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 EP EP13815445.5A patent/EP2954192B1/en active Active
- 2013-12-16 CN CN201380072317.XA patent/CN104981605B/en active Active
- 2013-12-16 WO PCT/EP2013/076667 patent/WO2014121870A1/en active Application Filing
Patent Citations (5)
| 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 |
| US20090145403A1 (en) * | 2007-12-05 | 2009-06-11 | Denso Corporation | Fuel supply system having fuel filter installed downstream of feed pump |
| US20090151700A1 (en) * | 2007-12-13 | 2009-06-18 | Denso Corporation | Backpressure valve and fuel system having the same |
| WO2012136429A1 (en) * | 2011-04-08 | 2012-10-11 | Robert Bosch Gmbh | Pump unit for supplying fuel, preferably diesel oil, from a containing tank to an internal combustion engine |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN111656001A (en) * | 2018-01-26 | 2020-09-11 | 德尔福知识产权有限公司 | Fuel pump |
| CN111656001B (en) * | 2018-01-26 | 2022-08-09 | 德尔福知识产权有限公司 | Fuel pump |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2954192A1 (en) | 2015-12-16 |
| EP2954192B1 (en) | 2017-10-25 |
| DE102013201892A1 (en) | 2014-08-07 |
| CN104981605B (en) | 2018-06-08 |
| WO2014121870A1 (en) | 2014-08-14 |
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