CN103133196A - System used for high-pressure injection system and provided with overflow valve and measuring unit - Google Patents
System used for high-pressure injection system and provided with overflow valve and measuring unit Download PDFInfo
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- CN103133196A CN103133196A CN2012104776807A CN201210477680A CN103133196A CN 103133196 A CN103133196 A CN 103133196A CN 2012104776807 A CN2012104776807 A CN 2012104776807A CN 201210477680 A CN201210477680 A CN 201210477680A CN 103133196 A CN103133196 A CN 103133196A
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- metering
- piston
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- pressure
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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
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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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0421—Cylinders
Abstract
The invention relates to a system (62) used for a high-pressure injection system (36) and provided with an overflow valve (41) and a measuring unit (37). The overflow valve (41) comprises a valve housing (45) having a valve barrel (44); a closed piston (46) capable of moving inside the valve housing (45) to open or close the overflow valve (41); and an elastic valve element (51) connected with the closed piston (46) and used for applying a pressure force, the direction of which is opposite to that of a pressure force applied by fluid inside a barrel chamber (66) onto the closed piston (46), onto the closed piston (46) so as to move the closed piston between closed and open positions by virtue of the pressure forces applied by the elastic valve element (51) and the fluid. The measuring unit (37) comprises a measuring housing (38) having a measuring barrel (69) and a measuring piston (53) capable of moving inside the measuring housing (38) to open or close the measuring unit (37), wherein the valve housing (45) and the measuring housing (38) are formed integrally.
Description
Technical field
The present invention relates to a kind of system with relief valve and batching unit for high-pressure injection system and a kind of high-pressure injection system.
Background technique
Be used for the high-pressure injection system of explosive motor, especially in diesel engine or petrolic common-rail injection system, high-pressure service pump is responsible for keeping the pressure in the high-pressure accumulator of common-rail injection system constantly.High-pressure service pump for example passes through the camshaft of explosive motor by drive shaft.To high-pressure service pump, use preposition transfer pump for transfer the fuel, for example gear pump or revolution proportioning pump, they are connected to the high-pressure service pump front.Preposition transfer pump flows to high-pressure service pump from fuel tank by fuel channel with fuel.
Also can use reciprocating pump as high-pressure service pump.Supporting one live axle in housing.Piston is set in cylinder perpendicularly.Place a roller with roller rolling surface having on the live axle of at least one cam, it is bearing in rotor seat.Rotor seat is connected with piston, makes piston be forced to carry out the oscillating type translational motion.Spring applies one with respect to live axle power diametrically on rotor seat, make roller be in all the time with live axle and contact.Roller contacts with live axle on the axle rolling surface on surface as the live axle with at least one cam by the roller rolling surface.Roller by sliding supported condition in rotor seat.
At this, live axle, roller and rotor seat with at least one cam are arranged in the lubricating chamber inside of high-pressure service pump.The fuel that flows to high-pressure service pump from preposition transfer pump is conducted through this lubricating chamber so that the parts of lubricated lubricating chamber inside on the one hand, and by the fuel that passes lubricating chamber's guiding cooling they.Therefore, the fuel that flows to high-pressure service pump by preposition transfer pump volume flow comprise the fuel that passes high-pressure service pump parts lubricating chamber's guiding, that be used for lubrication and cooling lubricating chamber inside and be included as that high-pressure service pump is determined, be used under high pressure flowing to the fuel of common rail.At this, to there be substantially invariable pressure on the fuel channel from preposition transfer pump to high-pressure service pump.Therefore one relief valve is set the fluid passage from preposition transfer pump to lubricating chamber.Higher than predetermined (for example 5.5bar) pressure the time, relief valve is opened, and more fuel is by lubricating chamber thus, and these fuel that pass lubricating chamber are fed to fuel tank again.When the pressure drop of relief valve front, for example lower than 4.5bar, relief valve cuts out.
This relief valve has closure piston, and it is bearing on cylinder between closed position and open position movingly.Fuel can be imported relief valve and can discharge from relief valve by tap hole by the inlet opening.Acting on the one hand the fuel pressure that has on the inlet opening on closure piston, spring force is arranged on the other hand.At this, act on power on closure piston, that caused by spring and fuel and point on the contrary, make in the situation that the different closure pistons of the fuel pressure on the inlet opening move at cylinder interior.At this, the tap hole that leads in the cylinder chamber that is surrounded by cylinder seals when closure piston is in the closed position.When only the pressure on the inlet opening improved by fuel, closure piston just moved to open position, and in this position, the tap hole on the cylinder chamber is not closed piston closes.
When the adjusting of suction side is directed to the fuel flow rate of common rail by high-pressure service pump, need batching unit, its controls and/or regulates the volume of fuel stream that is directed to high-pressure service pump.Generally can not control the transmission power of preposition transfer pump, but have batching unit.Batching unit comprises movable metering piston, and it is moved between closed position and open position by electromagnet and Spring driving.Can control and/or be adjusted to the volume of fuel stream of high-pressure service pump according to the endurance difference of closed position or open position.
At this, not only relief valve but also batching unit all need as element of construction independently to make it make the generation fringe cost to high-pressure service pump, the interface that separates of high-pressure service pump housing especially.In addition, relief valve and batching unit have housing separately.
DE 10 2,009 026 596 A1 illustrate a kind of for delivery of fluid, the high-pressure service pump of fuel especially, comprise a live axle, at least one piston, at least one cylinder for supporting piston, wherein, this at least one piston is bearing at least one cam indirectly or directly, makes at least one piston to carry out translational motion based on rotatablely moving of live axle.
Summary of the invention
have a relief valve and a batching unit according to the system for high-pressure injection system of the present invention, this relief valve comprises that one has the valve chest of valve barrel, one closure piston that can move between closed position and open position in valve chest inside, make in closed position relief valve close and in open position relief valve open, also has a flexible valve element that is connected with closure piston, especially valve spring, can exert pressure on closure piston by it, this pressure is directed against the pressure that the fluid by the cylinder chamber interior is applied on closure piston, make closure piston by being applied to the pressure on closure piston and can moving between closed position and open position by flexible valve element and fluid, described batching unit comprises that one has the metering housing of metering cylinder, one at metering enclosure interior movable metering piston between closed position and open position, make when closed position batching unit close and when open position batching unit open, wherein, described valve chest consists of integratedly with the metering housing.Therefore, described relief valve and batching unit be an element of construction advantageously, make when making this system, especially this system and high-pressure service pump, especially with the high-pressure service pump housing mechanically be connected when being connected, only need be fixed on an element of construction on high-pressure service pump.Can save in addition the cost when making this system, because only a member not only forms the metering housing but also forms valve chest.Thus, for example can save most of cost when moulding and/or when cutting, because only need make and process a member for metering housing and valve chest.
In further expanding structure, described closure piston can be bearing on valve barrel and described metering piston can be bearing on metering cylinder on the metering cylinder axial direction with moving to motion on the valve barrel axial direction, and, described valve barrel axis with respect to the metering cylinder axis with an acute angle, especially directed less than the angle of 30 °.
In one replenishes modification, described closure piston can be bearing on valve barrel and described metering piston can be bearing on metering cylinder on the metering cylinder axial direction with moving to motion on the valve barrel axial direction, and described valve barrel axis is basically parallel to the metering cylinder axis orientation.Orientation means substantially parallel, and described valve barrel axis and metering cylinder axis are directed in parallel to each other with the deviation less than 5 ° or 3 °, and especially mutual exactly parallel ground is directed.Therefore, this system's work in-process is simple especially and cost is favourable, makes because valve barrel and metering cylinder can cut especially simply.
Described valve barrel axis and described metering cylinder axis meet the destination separate less than 5cm, especially less than 1cm apart from mutual orientation, and same axis preferably.
In further mode of execution, described relief valve comprises an overflow inlet opening, as the inlet opening that is used for transporting fluid into the cylinder chamber interior of being surrounded by valve barrel, and described batching unit comprises that one measures the inlet opening, as the inlet opening that is used for transporting fluid into the cylinder chamber interior of being surrounded by metering cylinder, and described overflow inlet opening is same mouthful with the metering inlet opening.Thus, for batching unit with for relief valve, only need an inlet opening and preposition transfer pump hydraulic connecting.
In a further modification, this system comprises only inlet opening, is used for fluid not only is transported to relief valve but also is transported to batching unit.
In an additional project, this system comprises that an overflow tap hole and of be used for discharging the fluid of the cylinder chamber that imports to valve barrel is used for discharging the metering tap hole of the fluid of the cylinder chamber that imports to metering cylinder.Said overflow tap hole and described metering tap hole are preferably in the metering housing and the described of valve chest only consists of on a member, and it forms system casing or system casing.
This system preferably includes two that separate, as to be respectively used to relief valve and batching unit tap holes.
In an additional aspects, described batching unit comprise one preferably electricity, be used for making the motion of metering piston motion, electromagnet especially, and, can apply a power by this motion on metering piston.The control unit of high-pressure injection system is controlled and/or is regulated this batching unit, namely controls and/or regulate the motion of this metering piston.This metering piston is driven by motion and moves between open position and closed position, and the time that metering piston is shown in an open position is longer, more fuel can be imported high-pressure service pump, and vice versa.This motion or motion actuator can be also piezoelectric elements.
In a mode of execution that replenishes, described batching unit comprises a flexible measuring element that is connected with metering piston, metering spring especially, can apply a pressure by it on metering piston, this pressure is preferably on the direction that fluid by metering cylinder cylinder chamber interior can be applied to the pressure on metering piston directed, makes this metering piston preferably by being applied in the opposite direction the power on metering piston and can moving between closed position and open position in one direction and by motion by elasticity measuring element and/or fluid.
Described valve barrel especially is made of metering cylinder, described elastic valve element is made of the elasticity measuring element, make this system preferably include only elastic element, and, described closure piston is made of metering piston, make this system preferably include only piston, and, described elasticity measuring element preferably can be driven and described metering piston preferably is connected with the elasticity measuring element and described elasticity measuring element is connected with described motion by described motion, makes metering piston indirectly pass through the elasticity measuring element and is connected with described motion.Therefore this system has only piston, and it not only forms metering piston but also forms closure piston, thus can saving member.In addition, this system only has the elastic element that had both formed the elasticity measuring element, also formed elastic valve element.
This system, especially described valve chest and/or described metering housing aptly at least in part, especially fully by metal, for example steel or aluminium and/or be made of plastics.
Comprise that according to the high-pressure injection system for explosive motor of the present invention one has high-pressure service pump, a relief valve, a batching unit, a preposition transfer pump, a high voltage rail of lubricating chamber, wherein, described relief valve and the described batching unit system that is configured to describe in this application.
In a modification, the metering housing of the valve chest of described relief valve and described batching unit at least in part, especially fully the housing by described high-pressure service pump forms and/or is integrated in this high-pressure service pump housing.
In one replenishes modification, control and/or regulate at the explosive motor run duration volume flow that is flowed to the fuel of high-pressure service pump by preposition transfer pump, its mode is to control and/or regulate the through flow cross section of the fluid passage from preposition transfer pump to high-pressure service pump by batching unit.If the transmission power of preposition transfer pump is controllable or adjustable, generally need not batching unit and control and/or regulate the volume flow of the fuel that is directed to high-pressure service pump by preposition transfer pump.If the transmission power of preposition transfer pump is not controllable and/or adjustable, generally undertaken these by batching unit.
In another modification, the transmission power that described preposition transfer pump is gear pump and/or this preposition transfer pump is controllable and/or adjustable and/or this preposition transfer pump is have the preposition transfer pump of motor, electricity and/or can come transfer the fuel with for example preposition discharge pressure between 3bar to 6bar by this preposition transfer pump.
Aptly, the transmission power of described preposition transfer pump be not controllable and/or adjustable and this preposition transfer pump by explosive motor mechanically, for example by the camshaft actuated of explosive motor.
Have high-pressure injection system according to explosive motor of the present invention, that be particularly useful for Motor Vehicle, wherein, the high-pressure injection system that this high-pressure injection system is configured to describe in this application.
Description of drawings
The below explains embodiments of the invention in detail by accompanying drawing.Accompanying drawing illustrates:
Fig. 1 is for delivery of the cross section of the high-pressure service pump of fluid,
Fig. 2 roller is together with the A-A section according to Fig. 1 of rotor seat and live axle,
The view of extremely simplifying of Fig. 3 high-pressure injection system,
The cross section of extremely simplifying of Fig. 4 high-pressure service pump and preposition transfer pump,
Fig. 5 has the first embodiment's the longitudinal section of the system of relief valve and batching unit,
Fig. 6 is according to the second embodiment's of the system of Fig. 5 longitudinal section.
Embodiment
The cross section of the high-pressure service pump 1 for delivery of fuel shown in Figure 1.This high-pressure service pump 1 is used for, and fuel, for example gasoline or diesel oil are under high pressure flowed to explosive motor 39.Can for example be in 1000 to 3000bar scope by the pressure that high-pressure service pump 1 produces.
High-pressure service pump 1 has live axle 2, and this live axle has two cams 3, and this live axle can be carried out around spin axis 26 and rotatablely move.Spin axis 26 is arranged in the drawing of Fig. 1 and perpendicular to the drawing of Fig. 2.Piston 5 is bearing in the cylinder 6 that is made of housing 8.Working room 29 is by cylinder 6, housing 8 and piston 5 gauges.Having the inlet passage 22 that enters valve 19 and the discharge route 24 with expulsion valve 20 leads in working room 29.Fuel flow into working room 29 by inlet passage 22, and fuel is under high pressure 29 outflows again from the working room by discharge route 24.Enter valve 19, the following formation of for example safety check: only have fuel can flow in working room 29, expulsion valve 20, the following formation of for example safety check: only have fuel can be from the working room 29 to flow out.The volume of working room 29 is because the reciprocal stroke motion of piston 5 changes.Piston 5 is bearing on live axle 2 indirectly.Fixing rotor seat 9 with roller 10 on the end of piston 5 or pump piston 5.At this, roller 10 can be carried out and rotatablely move, and its spin axis 25 is arranged according to the drawing of Fig. 1 and perpendicular to the drawing of Fig. 2.Live axle 2 with at least one cam 3 has axle rolling surface 4, and roller 10 has roller rolling surface 11.Roller 10 is bearing on rotor seat 9 by sliding bearing 13.
The roller rolling surface 11 of roller 10 rolls at surface of contact 12 places on the axle rolling surface 4 of the live axle 2 with two cams 3.That rotor seat 9 is bearing in is that form by housing 8, in the rotor seat bearing as sliding bearing.Spring 27 or helical spring 27 are exerted pressure on rotor seat 9 as the elastic element 28 that is clamped between housing 8 and rotor seat 9, make the roller rolling surface 11 of roller 10 contact lastingly with the axle rolling surface 4 of live axle 2.Therefore, the common oscillating type stroke motion of carrying out of rotor seat 9 and piston 5.Roller 10 is bearing in rotor seat 9 by sliding bearing 13.
With the schematic diagram of extremely simplifying, high-pressure injection system 36 for the Motor Vehicle (not shown) is shown in Fig. 3, has high voltage rail 30 or fuel rail 31.From common rail or fuel rail 31, fuel is ejected into the firing chamber (not shown) of explosive motor 39 by the valve (not shown).Preposition transfer pump 35 uncontrollable, electronic aspect transmission power flows to high-pressure service pump 1 from fuel tank 32 by fuel channel 33 with fuel.An axle of explosive motor 39, for example bent axle or camshaft in these high-pressure service pump 1 driven shaft 2 drivings and live axle 2.The volume of fuel that time per unit is directed to high-pressure service pump 1 is controlled and/or regulated to batching unit 37.High voltage rail 30 is used for injecting fuel into the firing chamber of explosive motor 39.At this, the fuel that is not needed by high-pressure service pump 2 draws by the fuel feedback pipeline 34 of optional dress again to be got back in fuel tank 32.Relief valve 41 is not shown in Fig. 3.
Fig. 4 illustrates the part of high-pressure injection system 36.Housing 8 inside formation one lubricating chamber 40 at high-pressure service pump 1.Be furnished with live axle 2, roller 10, rotor seat 9(not shown in Fig. 4 in lubricating chamber 40) and be furnished with the part of piston 5.The fuel that guides by passing lubricating chamber 40, parts 2,5,9 and 10 by fuel lubricated.Have fluid passage 43 in housing 8 inside, by fluid passage 43, fuel being imported in lubricating chamber 40 and then derives again for this reason, and is flowing to fuel tank 32(Fig. 4 by fuel feedback pipeline 34 after discharging from lubricating chamber 40 again).Be shown in greater detail in high-pressure injection system 36 shown in Figure 3 in Fig. 4, there is no high voltage rail 30 and explosive motor 39.Preposition transfer pump 35 is uncontrollable aspect transmission power and/or adjusting in the embodiment shown in fig. 4, and drives by explosive motor 39.Preposition transfer pump 35 is configured to gear pump 14, for example internal gear pump 15 or external gear pump 16, and illustrate extremely simplifiedly.By preposition transfer pump 35 from the fuel of fuel tank 32 sucking-offs by preposition transfer pump 35 with preposition discharge pressure, for example 4bar, flow to high-pressure service pump 1 by fuel channel 33, namely flows to the inlet passage 22 of high-pressure service pump 1.In addition, the fuel of being carried by preposition transfer pump 35 flows to lubricating chamber 40 at explosive motor 39 run durations by relief valve 41 and the fluid passage 43 that is connected in relief valve 41 back and is used for lubricated for example live axle 2, roller 10 and piston 5.After fuel flow was crossed lubricating chamber 40, fuel flowed to fuel tank 32 by fluid passage 43 and fuel feedback pipeline 34 again.Can lubricate thus and also can cooling these parts 2,5,9 and 10.At this, the following formation of relief valve 41: have constant pressure in the fuel channel 33 of relief valve 41 fronts, as the preposition discharge pressure of 4.5bar.At this, preposition transfer pump 35 is also carried the additional fuel quantity that is used for lubricated high-pressure service pump 1 except carrying for the fuel delivery of high-pressure service pump 1, namely flows through the fuel of lubricating chamber 40.Pressure when increasing for fear of the transmission power at preposition transfer pump 35 on the fuel channel 33 of relief valve 41 fronts raises, when the fuel pressure in relief valve 41 fronts raises, for example from the pressure of 5.5bar, relief valve 41 is additionally opened, the fuel that is by relief valve 41 provides larger through flow cross section, until there is the pressure of 4.5bar in relief valve 41 fronts again.During lower than 4.5bar, relief valve 41 cuts out when the pressure in the fuel channel 33 of relief valve 41 fronts.Can provide substantially invariable at explosive motor 39 run durations in the fuel channel 33 of relief valve 41 fronts thus, be in the preposition discharge pressure between 4.5bar to 5.5bar, even the transmission power of preposition transfer pump 35 fluctuates slightly and explosive motor 39 has different demand for fuel.
Shown in Figure 5 for high-pressure injection system 36, the first embodiment that have the system 62 of relief valve 41 and batching unit 37.Relief valve 41 has valve chest 45, its gauge valve barrel 44.At valve barrel 44 interior support closure pistons 46.Closure piston 46 can be due to sliding bearing in the axial motion of carrying out on valve barrel 44 on valve barrel axis 54 directions, that is, on the contrary according to the view in Fig. 5 from left to right or.Valve barrel 44 or valve chest 45 surrounds cylinder chamber 66.Be processed with piston channel 47 in closure piston 46.The metering housing 38 of valve chest 45 and batching unit 37 is configured to system casing integratedly.Consist of passage 49 in this system casing, by it, fuel flow in system 62 by an inlet opening 58.At this, inlet opening 58 not only forms the overflow inlet opening 56 of relief valve 41 in the outside in Fig. 5, and forms the metering inlet opening 57 of batching unit 37.On the end of the passage 49 that branch is arranged, fuel flow into by flowing in cylinder chamber 66 by metering housing 38 gauges in the cylinder chamber 66 of valve barrel 44 gauges and by metering inlet opening 57 by overflow inlet opening 56.Be provided with valve spring 52 as flexible valve element 51 in closure piston 46 left sides in 66 inside, cylinder chamber on relief valve 41.At this, flexible valve element 51 is at one end fixed or is arranged on valve chest 45, is arranged on closure piston 46 at the other end.
The closed position of closure piston 46 shown in Figure 5.At this, fuel flow on overflow inlet opening 56 by passage 49 in cylinder chamber 66.If fuel pressure continues to improve on closure piston 46 right sides in cylinder chamber 66, for example bring up to the value over 5bar, because the fuel pressure in this part of cylinder chamber 66 is larger, closure piston 46 is against being continued to left movement by valve spring 52 applied pressures, make piston channel 47 overlap (not shown) with overflow tap hole 59 on its end, thus, fuel flows out from the overflow tap hole 59 as tap hole 61 by piston channel 47, arrives lubricating chamber 40.When pressure drop, closure piston 46 moves right so many, until do not exist the end that overlaps and make thus passage 7 by valve chest 45 sealings (Fig. 5) between the end of overflow tap hole 59 and piston channel 47, and do not have thus fuel flow to cross relief valve 41.Therefore, the power that is applied on closure piston 46 by valve spring 52 is reverse with the power that is applied on closure piston 46 right parts by fuel.
In batching unit 37, with the similar mode of relief valve 41, metering piston 53 sliding bearings the metering housing 38 metering cylinder 69 on.Be processed with the piston channel 48 of metering piston 53 in metering piston 53.Metering piston 53 supports to such an extent that can move on the direction of metering cylinder axis 55.Flexible measuring element 67 as metering spring 68 on first end on the metering inlet opening 57 upper supports metering housings 38 as inlet opening 58, at the second end upper support on the left part of metering piston 53.The open position of metering piston 53 shown in Figure 5 makes fuel to flow out from the metering tap hole 60 as tap hole 61 by piston channel 48.Metering piston 53 is connected with motion 63 as electromagnet 64 indirectly by bearing pin 65 on its right part.Can apply by electromagnet 64 and bearing pin 65 power of pointing to left on metering piston 53, make metering piston 53 against be applied to by metering spring 68 on metering piston 53 power and against being applied to the power on metering piston 53 left parts by fuel and moving to the closed position (not shown) left, make metering tap hole 60 not overlap with the end of piston channel 48 and not have thus fuel can flow through piston channel 48, piston 53 is closed because metering tap hole 60 is measured.Electromagnet 64 is controlled by the unshowned control unit of high-pressure injection system 36, and metering piston 53 moves between open position and closed position.The time that metering piston 53 is shown in an open position is longer, and more fuel enters into high-pressure service pump 1, and vice versa.
The second embodiment of system 62 shown in Figure 6.Below the main difference of describing with the first embodiment.System 62 comprises only piston 46,53, and this piston not only forms closure piston 46 but also forms metering piston 53.Be processed with the piston channel 47,48 of closure piston 46 and metering piston 53 in this piston 46,53.Flexible valve element 51 also forms flexible measuring element 67.Flexible valve element 51 or measuring element 67 the first end upper support on the left side on piston 46,53 and at the second end upper support on the right side on latch plate 50 or be fixed on latch plate 50.Latch plate 50 can be by electromagnet 64 motion as motion 63 on the direction of valve barrel axis and metering cylinder axis 54,55 because bearing pin 65 not only with latch plate 50 mechanical connections, and with electromagnet 64 mechanical connections.The closed position of piston 46,53 shown in Figure 6.Overflow tap hole 59 on cylinder chamber 66 is hidden by piston 46,53, at piston channel 47, do not exist between 48 end and overflow tap hole 59 and overlap, making does not have fuel can be in piston 46,53 left sides flow out by piston channel 47,48 and flow out from overflow tap hole 59 from cylinder chamber 66.When electromagnet 64 energising, latch plate 50 moves to the left side end position shown in Fig. 6, and when electromagnet 64 outage, latch plate 50 moves to unshowned right side end position.Be in the left side during end position at latch plate 50, by flexible valve element 51 or measuring element 67 apply on piston 46,53 one that point to left, than power larger when latch plate 50 is in the right side end position.In addition.Act on the left part of piston 46,53 in the fuel pressure of 66 inside, cylinder chamber in piston 46,53 left sides and apply a power of pointing to the right on piston 46,53, namely reverse with the power that is applied on piston 46,53 by flexible valve element 51 or measuring element 67.Fuel pressure on inlet opening 58 and cylinder chamber 66 on piston 46,53 left sides is larger, and piston moves manyly towards the open position (not shown) to the right.For this reason, valve barrel 44 or metering cylinder 69 have the backstop for the piston 46,53 that is shown in an open position.At this open position, fuel can and flow to lubricating chamber 40 by overflow tap hole 59 by piston channel 47,48.Latch plate 50 be in the left side end position time longer, larger for making piston 46,53 move to the required fuel pressure of open position, vice versa.By the metering tap hole 60 on system casing, fuel flow is to high-pressure service pump 1.Therefore there is the relief valve 41 with variable pressure.Control unit make latch plate 50 remain on the left side end position time longer, the pressure that fuel flows to high-pressure service pump 1 is larger, vice versa.The unwanted fuel of high-pressure service pump 1 is due to the motion of fuel pressure and the piston 46,53 that causes thus and flow to lubricating chamber 40 by overflow tap hole 59.
In a word, according to system 62 of the present invention with according to high-pressure injection system 36 of the present invention, obvious advantage is arranged.This system 62 only has a system casing and this system casing consists of integratedly, and wherein, this system casing is made of the valve chest 45 of relief valve 41 and the metering housing 38 of batching unit 37.Produce thus lower cost when processing system 62.In addition, this system casing is formed by the housing 8 of high-pressure service pump 1, makes advantageously and need not independent system casing for system 62.Thus, when manufacturing system 62, basic only the need is worked into passage 49, valve barrel 44 and metering cylinder 69 in housing 8 and then valve spring 52, metering spring 68, closure piston 46, metering piston 53 and motion 63 fixed and are arranged on housing 8 or system casing on housing 8.Metering tap hole 60 enters valve 19 by what passage 49 directly led to high-pressure service pump 1, and overflow tap hole 59 directly leads to lubricating chamber 40 by the fluid passage 43 in housing 8.The inlet opening 58 and preposition transfer pump 35 hydraulic connectings that only consist of on housing 8.
Claims (14)
1. be used for the system (42) of high-pressure injection system (36), have relief valve (41) and have batching unit (37), this relief valve (41) comprising:
One has the valve chest (45) of valve barrel (44),
One closure piston (46) that can move between closed position and open position in valve chest (45) inside, make relief valve when closed position (41) be close and when open position relief valve (41) open,
One elastic valve element (51) that is connected with closure piston (46), valve spring (52) especially, can apply a pressure on closure piston (46) by it, this pressure with can be directed by the pressure reversal ground that the inner fluid in cylinder chamber (66) be applied on described closure piston (46), make the closure piston (46) can be by being applied to the pressure on this closure piston (46) and moving between closed position and open position by this elastic valve element (51) and described fluid
Described batching unit (37) comprising:
One has the metering housing (38) of metering cylinder (69),
One metering piston (53) that can move between closed position and open position in metering housing (38) inside, make when closed position this batching unit (37) be close and when open position this batching unit (37) open,
It is characterized in that, described valve chest (45) consists of integratedly with described metering housing (38).
2. the system as claimed in claim 1, it is characterized in that, described closure piston (46) can be bearing on motion ground on valve barrel axis (54) direction that described valve barrel (44) is gone up and described metering piston (53) can be bearing on described metering cylinder (69) with moving on metering cylinder axis (55) direction, and described valve barrel axis (54) is in an acute angle with respect to described metering cylinder axis (55), especially directed less than the angle ground of 30 °.
3. the system as claimed in claim 1, it is characterized in that, described closure piston (46) is in the upper motion ground supporting on valve barrel axis (54) direction of valve barrel (44), and described metering piston (53) is in the upper motion ground supporting on metering cylinder axis (55) direction of metering cylinder (69), and described valve barrel axis (54) is basically parallel to metering cylinder axis (55) calibration.
4. system as claimed in claim 3, is characterized in that, described valve barrel axis (54) and described metering cylinder axis (55) with less than 5cm, especially less than 1cm apart from mutual orientation, same axis preferably.
5. system as described in any one in above-mentioned claim, it is characterized in that, described relief valve (41) comprises an overflow inlet opening (56), as being used for transporting fluid into the inner inlet opening (58), cylinder chamber (66) that is surrounded by valve barrel (44), described batching unit (37) comprises that one measures inlet opening (57), as being used for transporting fluid into the inner inlet opening (58), cylinder chamber (66) that is surrounded by metering cylinder (69), and described overflow inlet opening (56) is with a bite with described metering inlet opening (57).
6. system as described in any one in above-mentioned claim, is characterized in that, this system (62) comprises an only inlet opening (58), is used for fluid not only is transported to relief valve (41) but also is transported to batching unit (37).
7. system as described in any one in above-mentioned claim, it is characterized in that, this system (62) comprises overflow tap hole (59) and the metering tap hole (60) for the fluid of discharging the cylinder chamber (66) that imports to metering cylinder (69) for the fluid of discharging the cylinder chamber (66) that imports to valve barrel (44).
8. system as described in any one in above-mentioned claim, is characterized in that, this system (62) comprises two that separate, as to be respectively used to relief valve (41) and batching unit (37) tap holes (61).
9. system as described in any one in above-mentioned claim, it is characterized in that, described batching unit (37) comprises motion (a 63) best electricity, that be used for making metering piston (53) motion, especially an electromagnet (64), and can apply a power on metering piston (53) by this motion (63).
10. system as described in any one in above-mentioned claim, it is characterized in that, described batching unit (37) comprises an elasticity measuring element (67) that is connected with metering piston (53), especially a metering spring (68), can exert pressure on metering piston (53) by it, this pressure is preferably in and is applied on the direction of the pressure on this metering piston (53) directed by the inner fluid in the cylinder chamber (66) of metering cylinder (69), make described metering piston (53) preferably by being applied in the opposite direction the power on this metering piston (53) and can moving between closed position and open position in one direction and by described motion (63) by elasticity measuring element (67) and/or this fluid.
11. system as described in any one in above-mentioned claim, it is characterized in that, described valve barrel (44) is formed by described metering cylinder (69) and described closure piston (46) is formed by described metering piston (53), make this system (62) comprise only piston (46, 53), described elastic valve element (51) is preferably formed by described elasticity measuring element (67), make this system (62) comprise only elastic element (51, 67), described elasticity measuring element (67) is preferably driven by motion (63), best described metering piston (53) is connected with described elasticity measuring element (67) and described elasticity measuring element (67) is connected with described motion (63), make described metering piston (53) indirectly be connected with described motion (63) by described elasticity measuring element (67).
12. system as described in any one in above-mentioned claim, it is characterized in that, this system (62), especially described valve chest (45) and/or described metering housing (38) at least in part, especially fully by metal, for example steel or aluminium and/or be made of plastics.
13. be used for the high-pressure injection system (36) of explosive motor (39), comprise:
One has the high-pressure service pump (1) of lubricating chamber (40),
One relief valve (41),
One batching unit (37),
One preposition transfer pump (35),
One high voltage rail (30),
It is characterized in that, described relief valve (41) and described batching unit (37) are configured to as any one in above-mentioned claim or multinomial described system (62).
14. high-pressure injection system as claimed in claim 13, it is characterized in that, the valve chest (45) of described relief valve (41) and the metering housing (38) of described batching unit (37) are at least in part, especially fully the housing (8) by described high-pressure service pump (1) forms.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE201110086690 DE102011086690A1 (en) | 2011-11-21 | 2011-11-21 | Operating system for high pressure injection system for e.g. diesel engine of motor car, has valve housing of overflow valve and measuring housing of measuring unit, which are formed integrally |
| DE102011086690.6 | 2011-11-21 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103133196A true CN103133196A (en) | 2013-06-05 |
| CN103133196B CN103133196B (en) | 2017-05-24 |
Family
ID=48221854
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210477680.7A Expired - Fee Related CN103133196B (en) | 2011-11-21 | 2012-11-21 | System used for high-pressure injection system and provided with overflow valve and measuring unit |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN103133196B (en) |
| DE (1) | DE102011086690A1 (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0077203A2 (en) * | 1981-10-10 | 1983-04-20 | Torotrak (Development) Limited | Fluid flow control valve |
| CN2328812Y (en) * | 1997-06-11 | 1999-07-14 | 毛自珍 | Hydraulic metering driving oil spray pump |
| CN1936335A (en) * | 2006-10-13 | 2007-03-28 | 彭利 | Flow.pressure combined control valve and pressure-limited, flow-limited hydraulic pump |
| CN101253459A (en) * | 2005-08-31 | 2008-08-27 | 卡特彼勒公司 | Metering valve with integral relief and makeup function |
| CN101387250A (en) * | 2007-09-11 | 2009-03-18 | C.R.F.索奇埃塔·孔索尔蒂莱·佩尔·阿齐奥尼 | Fuel injection system comprising a variable flow rate high-pressure pump |
| DE102008015546A1 (en) * | 2008-03-25 | 2009-10-01 | Robert Bosch Gmbh | Fuel injection system i.e. diesel injection system, for internal-combustion engine, has multi-function valve device provided with valve piston, which represents function of metering device and function of pressure control valve |
| CN101828025A (en) * | 2008-06-19 | 2010-09-08 | 博世汽车柴油系统股份有限公司 | High pressure pump assembly for common rail system |
Family Cites Families (1)
| 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 |
-
2011
- 2011-11-21 DE DE201110086690 patent/DE102011086690A1/en not_active Withdrawn
-
2012
- 2012-11-21 CN CN201210477680.7A patent/CN103133196B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0077203A2 (en) * | 1981-10-10 | 1983-04-20 | Torotrak (Development) Limited | Fluid flow control valve |
| CN2328812Y (en) * | 1997-06-11 | 1999-07-14 | 毛自珍 | Hydraulic metering driving oil spray pump |
| CN101253459A (en) * | 2005-08-31 | 2008-08-27 | 卡特彼勒公司 | Metering valve with integral relief and makeup function |
| CN1936335A (en) * | 2006-10-13 | 2007-03-28 | 彭利 | Flow.pressure combined control valve and pressure-limited, flow-limited hydraulic pump |
| CN101387250A (en) * | 2007-09-11 | 2009-03-18 | C.R.F.索奇埃塔·孔索尔蒂莱·佩尔·阿齐奥尼 | Fuel injection system comprising a variable flow rate high-pressure pump |
| DE102008015546A1 (en) * | 2008-03-25 | 2009-10-01 | Robert Bosch Gmbh | Fuel injection system i.e. diesel injection system, for internal-combustion engine, has multi-function valve device provided with valve piston, which represents function of metering device and function of pressure control valve |
| CN101828025A (en) * | 2008-06-19 | 2010-09-08 | 博世汽车柴油系统股份有限公司 | High pressure pump assembly for common rail system |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102011086690A1 (en) | 2013-05-23 |
| CN103133196B (en) | 2017-05-24 |
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Granted publication date: 20170524 Termination date: 20191121 |