EP2687712B1 - Ventilanordnung - Google Patents

Ventilanordnung Download PDF

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Publication number
EP2687712B1
EP2687712B1 EP12177133.1A EP12177133A EP2687712B1 EP 2687712 B1 EP2687712 B1 EP 2687712B1 EP 12177133 A EP12177133 A EP 12177133A EP 2687712 B1 EP2687712 B1 EP 2687712B1
Authority
EP
European Patent Office
Prior art keywords
armature
valve member
valve assembly
inlet valve
assembly according
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.)
Active
Application number
EP12177133.1A
Other languages
English (en)
French (fr)
Other versions
EP2687712A1 (de
Inventor
Michel Marechal
Raphael Rouillon
Etienne Pereira
Thierry Antuna
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Delphi International Operations Luxembourg SARL
Original Assignee
Delphi International Operations Luxembourg SARL
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Delphi International Operations Luxembourg SARL filed Critical Delphi International Operations Luxembourg SARL
Priority to EP12177133.1A priority Critical patent/EP2687712B1/de
Priority to HUE12177133A priority patent/HUE025798T2/en
Publication of EP2687712A1 publication Critical patent/EP2687712A1/de
Application granted granted Critical
Publication of EP2687712B1 publication Critical patent/EP2687712B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F02M59/368—Pump inlet valves being closed when actuated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F02M63/0021—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures
    • F02M63/0022—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures the armature and the valve being allowed to move relatively to each other
    • 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
    • F04B1/0452—Distribution members, e.g. valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0465—Distribution members, e.g. valves plate-like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/102—Disc valves
    • F04B53/103—Flat-annular type disc valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • F02M2200/502—Springs biasing the valve member to the open position

Definitions

  • the present invention relates to an inlet valve assembly suitable for use in a fuel pump.
  • the invention relates to an inlet valve assembly for a pump head of a high-pressure fuel pump for use in a common rail fuel injection system.
  • High-pressure fuel pumps for common rail fuel injection systems typically comprise one or more hydraulic pump heads in which fuel is pressurised in a pumping chamber of the pump head by the reciprocating movement of a plunger.
  • low-pressure fuel is delivered to the pump head by a low-pressure lift pump in the fuel tank and/or by a transfer pump built into the high-pressure fuel pump.
  • the low-pressure fuel is drawn into the pumping chamber through an associated inlet valve on a filling or return stroke of the plunger, during which the volume of the pumping chamber increases.
  • the inlet valve closes and the volume of the pumping chamber decreases, resulting in an increase in the fuel pressure within the pumping chamber.
  • an outlet valve associated with the pumping chamber opens to allow the high-pressure fuel out of from the pumping chamber to the common rail for delivery to the fuel injectors.
  • the fuel pressure in the common rail which determines the fuel injection pressure, may be varied from a moderate pressure of a few hundred bar at low engine loads and speeds to a very high pressure of up to 3000 bar or more at high engine loads and speeds.
  • an additional control valve known as an inlet metering valve, may be provided upstream of the inlet valve of the pumping chamber.
  • the inlet metering valve is used to control the amount of fuel that enters the pumping chambers of the fuel pump, and consequently the quantity of fuel that is compressed and delivered to the common rail at high pressure with each plunger stroke.
  • a conventional inlet metering valve is effectively a controllable orifice, which acts to throttle the flow of fuel to the inlet valve of the high-pressure pump. In this way, only the amount of fuel required by the engine is delivered to the rail, thereby saving both fuel and energy compared to the situation where fuel is fed by the lift or transfer pump at constant full delivery.
  • the inlet metering valve is under the control of the engine control unit, which determines the desired rail pressure and the actual rail pressure and adjusts the inlet metering valve accordingly.
  • inlet metering valves can be expensive and add to the overall cost of the common rail injection system, which is undesirable.
  • inlet metering valves are relatively large and space-consuming components.
  • inlet metering valves can be vulnerable to wear and to damage due to low-quality fuels.
  • the use of a conventional inlet metering valve means that the metering/rail pressure control mechanism is relatively far from the pumping chamber of the high-pressure fuel pump, which leads to undesirable delays in rail pressure control.
  • the inlet valve for the pumping chamber is provided with an actuator arrangement which allows the inlet valve to be closed in response to a signal from the engine's electronic control unit.
  • the quantity of fuel that enters the pumping chamber during the filling stroke of the plunger can be regulated without the need for an additional inlet metering valve.
  • Such arrangements are described in DE 10 2008 018 018 , GB 2 180 039 A and EP 1921307 .
  • EP 1921307 also describes the use of the inlet valve as a spill valve to return high-pressure fuel from the pumping chamber to the fuel rail during the pumping stroke of the plunger.
  • electronically-controllable or switchable inlet valves are actuated by a solenoid actuator arrangement operable to control the movement of a poppet-type inlet valve member that is received within a bore in the pump head.
  • An armature is attached to a valve stem of the valve member, and a head portion of the valve member is engageable with an associated seating formed at the end of the bore.
  • the performance of such solenoid-actuated inlet valves can be compromised by several factors.
  • the inlet valve is in its fully-open position, it is desirable that the cross-sectional area available for fuel to flow between the valve head and the valve seat is as large as possible, to maximise the flow of fuel into the pumping chamber at high engine loads.
  • the stroke of the valve member between its fully-open position and its fully-closed position must be relatively long. This, in turn, means that the air gap between the armature and the core is relatively large when the valve is fully open. Since the force applied to the armature of a solenoid actuator decreases significantly as the air gap increases, a relatively large and expensive solenoid must be used to achieve the force necessary to close the valve.
  • the armature is typically in the form of a collar that is press-fitted or otherwise attached to the valve stem. Any variation in concentricity between the armature and the valve stem, and between the armature and the core, can result in undesirable side-loads that can cause excessive wear of the valve member and the valve seat during the service life of the inlet valve. Because the inlet valve is subject to very high fuel pressures, such wear can seriously impair the performance and reliability of the valve. The inlet valve must therefore be manufactured with very tightly-controlled tolerances in the dimensions and concentricity of the parts, which increase manufacturing complexity and cost.
  • the present invention resides in an inlet valve assembly for a high-pressure fuel pump, comprising an inlet valve member moveable between open and closed positions to control the fuel flow from a source of low-pressure fuel to a pumping chamber of the fuel pump, and an electromagnetic actuator comprising a core member, a solenoid coil, and an armature moveable towards the core member in response to energisation of the coil.
  • the armature In a first phase of operation, the armature is decoupled from the valve member to allow movement of the armature towards the core member without movement of the valve member.
  • the armature is coupled to the valve member to carry the valve member towards its closed position.
  • the armature can move independently of the valve member in the first phase of operation, any variations in concentricity between the valve member, the armature, the core member and/or other components of the valve assembly can be accommodated more readily than if the armature were fixedly attached to the valve member. As a result, the dimensional tolerances of the components of the valve assembly are less critical, and so the cost and complexity of manufacturing the valve assembly can be reduced.
  • an annular clearance is defined between the armature and the valve member.
  • the armature is generally tubular, and the annular clearance is defined, in part, by an internal collar of the armature.
  • the valve member carries a lift collar, and the armature is arranged to engage with the lift collar to couple the armature to the valve member in the second phase of operation.
  • the armature when the armature is tubular and includes an internal collar, the internal collar of the armature may engage with the lift collar.
  • the lift collar may include an outwardly-directed flange, and a part of the armature (for example the internal collar, when provided) may engage with the flange.
  • the lift collar is preferably press-fitted or crimped onto the valve member.
  • the inlet valve assembly further comprises a biasing spring to bias the valve member into its open position.
  • the lift collar functions as a spring seat for the biasing spring.
  • the biasing spring may act on a first side of the flange, and the internal collar of the armature may act on a second, opposite side of the flange.
  • Stop means may be provided for limiting the opening movement of the valve member.
  • the stop means comprises a stop member carried on the valve member.
  • the stop member may be arranged to stop against a housing part of the fuel pump to limit the opening movement of the valve member.
  • the stop member may be disposed between the armature and the valve member and, advantageously, the stop member may be made from a non-magnetic material. With this arrangement, the stop member helps to prevent the magnetic field circuit that arises upon energisation of the coil from entering the valve member, thereby increasing the efficiency of the actuator.
  • the stop member comprises a tubular sleeve or collar.
  • the stop member may include an outwardly-directed flange for engagement with a housing part of the fuel pump.
  • the stop member may also limit movement of the armature away from the core.
  • the stop member may be press-fitted or crimped onto the valve member.
  • a non-magnetic spacer member may be disposed between the armature and the core.
  • the spacer member may, for example, comprise a non-magnetic washer affixed to the armature.
  • the core member may include an extended portion that overlaps with the armature during at least a part of the range of movement of the armature.
  • the maximum gap between the core member and the armature can be larger, for a given core and armature size, than would be the case if no extended portion were present.
  • the range of movement of the valve member can be relatively large, maximising the rate at which fuel can flow through the inlet valve assembly to fill the pumping chamber.
  • the presence of the extended portion of the core member allows a smaller coil to be used than would otherwise be the case.
  • the size of the valve assembly can be reduced.
  • the extended portion preferably overlaps with the armature along the axis of movement of the armature over the whole range of movement of the armature.
  • the extended portion may, for example, comprise an annular projection that extends from a face of the core member.
  • the extended portion preferably defines a recess that receives, in part, the armature.
  • the inlet valve assembly may include an outer pole.
  • the outer pole may include an aperture for receiving the armature, and movement of the armature may be guided by the aperture.
  • the outer pole may be arranged to retain the core member.
  • the core member may comprise a flange, and the outer pole may include a slot to receive the flange.
  • the outer pole may be generally cup-shaped.
  • the outer pole includes a base, and the base includes the aperture through which the armature is received.
  • the inlet valve assembly of the present invention is preferably adapted for use with a pump head of a high-pressure fuel pump.
  • the inlet valve assembly may be adapted to engage with a housing of a pump head.
  • the outer pole may comprise a mounting flange for mounting the inlet valve assembly to the pump head housing.
  • a pump head for a high pressure fuel pump comprising an inlet valve assembly according to the above-described aspect of the invention may also be provided. Furthermore, a fuel pump having at least one such pump head can also be contemplated.
  • Figure 1 shows, in part, a pump head 10 comprising a head housing 12 and an inlet valve assembly 14 mounted on the head housing 12.
  • the head housing 12 defines a plunger bore for receiving a plunger that reciprocates in use along a pumping axis A to cyclically increase and decrease the volume of a pumping chamber 16 (only the upper end of which can be seen in Figure 1 ).
  • the upper end of the head housing 12 comprises a generally cylindrical turret portion 18. As will be explained in more detail below, parts of the inlet valve assembly 14 cooperate with the turret to connect the inlet valve assembly 14 to the head housing 12.
  • the pumping chamber 16 is formed as a bore in the head housing 12. During a return stroke of the plunger, fuel can be drawn into the pumping chamber 16 by way of an inlet bore 20.
  • the inlet bore 20 communicates, by way of a drilling 22, with an annular space 24 formed by an annular v-shaped groove 26 in the top of the turret portion 18.
  • the annular space 24 receives fuel at low pressure by way of inlet passages (not shown).
  • valve member 28 of the inlet valve assembly 14 The flow of fuel between the inlet bore 20 and the pumping chamber 16 is regulated by a poppet valve member 28 of the inlet valve assembly 14. At its lowest end, the valve member 28 is formed into a valve head 30 with a relatively large diameter. The remainder of the valve member 28 forms a valve stem 32. A frustoconical seating surface 34 extends from the valve head 30 to the valve stem 32, and the seating surface 34 is engageable with a frustoconical valve seat 36 formed in the head housing 12 where the pumping chamber 16 meets the inlet bore 20. In Figure 1 , the valve member 28 is shown in its open position, with the seating surface 34 disengaged from the valve seat 36 to allow fuel to enter the pumping chamber 16.
  • the stem 32 of the valve member 28 extends upwardly from the valve head 30 through a guide bore 38 formed in the head housing 12.
  • a guide portion 40 of the stem 32 has a suitable diameter to form a sliding fit in the guide bore 38, so that movement of the valve member 28 is guided in an axial direction.
  • the guide bore 38, and hence the direction of movement of the valve member 28, is coaxial with the pumping axis A.
  • the actuator arrangement 50 generally comprises a core member 52, a solenoid coil 54, an outer pole 56, and a moveable armature 58.
  • the outer pole 56 is mounted to the head housing 12 and is arranged to retain the core member 52 in a position spaced from the head housing 12, and the coil 54 and the armature 58 are disposed between the core member 52 and the head housing 12.
  • the outer pole 56 comprises a generally cup-shaped body having a base 56a and a generally cylindrical wall 56b extending upwardly from the base 56a.
  • a mounting flange or lip 56c extends downwardly from the base 56a to embrace the turret portion 18 of the head housing 12.
  • An o-ring 60 forms a seal between the turret portion 18 and a chamfered part of the lip 56c, to prevent fuel leakage from the valve assembly 14.
  • the core member 52 comprises a generally tubular central portion 52a, surrounded by an annular flange 52b.
  • the flange 52b extends outwardly from the central portion 52a to mate with an annular slot 56d formed in the inside surface of the wall 56b of the outer pole 56.
  • the uppermost edge 56e of the wall 56b is crimped over the flange 52b to retain the flange 52b in the slot 56d.
  • the coil 54 is wound around a coil former 62, preferably of plastics material.
  • the coil former 62 is ring-shaped, and the central portion 52a of the core member 52 is received in the centre of the ring.
  • the coil former 62 therefore surrounds the central portion 52a of the core member 52, and is disposed between the flange 52b of the core member 52 and the base 56a of the outer pole 56.
  • the coil 54 is received within an annular channel 64 formed in the outer face of the coil former 62.
  • the centre of the coil former 62 is in fluid communication with the annular space 24 through which low-pressure fuel is delivered to the pumping chamber 16.
  • the coil former 62 forms a seal with the flange 52b of the core member 52 at its upper end and with the base 56a of the outer pole 56 at its lower end, with respective o-rings 66, 68 being provided to effect the seals.
  • the armature 58 is generally tubular, having an outer wall 58a and an inner bore 58b through which the stem 32 of the valve member 28 extends.
  • the armature has an inwardly-extending collar 58c, provided at an intermediate position along the bore 58b, defining a restricted-diameter region within the bore 58b.
  • the armature 58 is not fixedly connected to the valve member 28, but instead the collar 58c of the armature 58 cooperates with the valve member 28 to transfer movement of the armature 58 to the valve member 28 as will be explained below.
  • the base 56a of the outer pole 56 includes a central aperture 56f for receiving the armature 58.
  • the outer wall 58a of the armature 58 is in sliding contact with the wall of the aperture 56f, so that the outer pole 56 guides axial movement of the armature 58 in use.
  • the tubular central portion 52a of the core member 52 extends downwardly, towards the armature 58. At its upper end, the tube that forms the central portion 52a is closed, so that the core member 52 acts as a cap for the valve assembly 14, and defines a cavity 52c within the central portion 52a for receiving a biasing spring 70 for the valve member 28.
  • An upper end of the spring 70 bears against the closed end of the cavity 52c, whilst an opposite, lower end of the spring 70 acts against a spring collar 72 mounted on an upper part 32a of the stem 32 of the valve member 28. In this way, the spring 70 biases the valve member 28 into its open position.
  • the spring collar 72 comprises a tubular sleeve which is press-fitted onto the upper part 32a of the stem 32. At its lowermost end, the spring collar 72 is flared outwardly to define a spring flange 72a.
  • the spring 70 bears on the upper surface of the spring flange 72a to apply a biasing force to the valve member 28 in its opening direction.
  • the stem 32 of the valve member 28 also carries a stop collar 74.
  • the stop collar 74 is press-fitted onto the stem 32 between the spring collar 72 and the guide portion 40 of the stem 32.
  • the stop collar 74 comprises a tubular sleeve with an outwardly-flared lowermost end, to define a stop flange 74a.
  • the stop flange 74a abuts a raised, central portion 76 of the turret 18 of the head housing 12 when the valve member 28 is in its open position, as shown in Figure 1 . In this way, the stop flange 74a acts as a stop member for limiting the opening movement of the valve member 28.
  • the spring flange 72a and the stop flange 74a are spaced apart along the axis of the valve member 28.
  • the internal collar 58c of the armature 58 extends into the gap between the spring flange 72a and the stop flange 74a.
  • the thickness of the internal collar 58c, in the direction of the pumping axis A, is less than the gap between the spring flange 72a and the stop flange 74a, so that the collar 58c is a clearance fit between the respective flanges 72a, 74a. This allows the armature 58 to move in the axial direction independently of the valve member 28 over a short distance corresponding to the total axial clearance between the collar 58c and the flanges 72a, 74a.
  • the internal diameter of the collar 58c of the armature 58 is larger than the external diameter of the tubular part of the stop collar 74, thereby to define an annular clearance 75 between the stop collar 74 and the collar 58c of the armature 58.
  • the collar 58c of the armature 58 does not therefore constrain the valve member 28 in the radial direction.
  • the lowermost face of the central portion 52a of the core member 52 includes a recess 52d.
  • the outer edge of the recess 52d is defined by a downwardly-extended portion 52e of the core member 52, in the form of an annular ridge or horn.
  • the inside diameter of the recess 52d is larger than the outside diameter of the armature 58, so that there is no radial contact between the armature 58 and the core member 52. Furthermore, a washer or spacer 78 of non-magnetic material is provided on the top face of the armature 58, to prevent direct contact between the armature 58 and the core member 52 and to guide the magnetic flux to enter the armature 58 radially, rather than axially.
  • the core member 52, the outer pole 56 and the armature 58 are preferably formed from a ferromagnetic material, such as mild steel. In this way, when the coil 54 is energised, the resulting magnetic flux is contained within a magnetic circuit defined by these ferromagnetic components.
  • the spring collar 72 and the stop collar 74 are made from a non-magnetic material, such as an austenitic stainless steel, which helps to stop the magnetic circuit from straying out of the armature 58 and into the valve member 28.
  • the armature 58 moves towards the core member 52. Initially, the armature 58 is decoupled from the valve member 28 so that, in a first phase of movement of the armature 58, the valve member 28 remains stationary in its fully open position under the influence of the biasing spring 70.
  • closing movement of the valve member 28 stops when the seating surface 34 of the valve member 28 meets the valve seat 36. Once the valve member 28 is seated, further upward movement of the armature 58 is blocked by the spring flange 72a, leaving a relatively small clearance between the top of the armature 58 and the core member 52 in the axial direction.
  • the armature 58 is initially decoupled from the valve member 28, and because there is an annular clearance 75 between the valve member 28 and the armature 58, movement of the armature 58 can occur without being constrained by the valve member 28. Consequently, any variations in concentricity and/or alignment between the valve member 28 and the armature 58 can be accommodated without any adverse effect on the operation of the valve assembly 14. Said another way, because the armature 58 is decoupled from the valve member 28 during a first phase of operation of the valve assembly, additional axial and radial degrees of freedom of movement are present compared to conventional arrangements in which the armature is fixedly attached to the valve member. These additional degrees of freedom allow compensation for misalignment and dimensional variations due to manufacturing tolerances.
  • the actuator arrangement of the embodiment of Figure 1 is effective even when the air gap between the armature 58 and the core member 52 is relatively large when the valve member 28 is fully open.
  • this allows the clearance between the seating surface 34 of the valve member 28 and the valve seat 36 to be maximised for a given actuator size, so as to provide a high flow rate of fuel into the pumping chamber 16 during the filling stroke of the pumping element.
  • the inlet valve assembly may be operated as follows. To fill the pumping chamber 16 during the filling stroke of the plunger, in which the plunger moves to increase the volume of the pumping chamber 16, the coil 54 is de-energised and the valve member 28 is held in its open position by the biasing spring 70 as shown in Figure 1 . Fuel is drawn into the pumping chamber 16 past the open valve member 28 as a result of the increase in volume of the pumping chamber 16.
  • An electronic control unit of the engine calculates the quantity of fuel that should be permitted to enter the pumping chamber 16 during each filling stroke, according to the current rail pressure and the demand for fuel based on the prevailing engine operating conditions.
  • the pumping stroke of the plunger begins to decrease the volume of the pumping chamber 16, thereby to increase the pressure of fuel in the pumping chamber 16.
  • Flow of fuel out of the pumping chamber 16 through the inlet valve is prevented by the seated valve member 28.
  • the fuel pressure in the pumping chamber 16 applies a force to the valve member 28 in the closing direction, which becomes sufficient to overcome the opening force applied to the valve member 28 by the spring 70.
  • the coil 54 can be de-energised to save energy: the valve member 28 remains in its closed position as a result of the fuel pressure in the pumping chamber 16.
  • the high-pressure fuel in the pumping chamber 16 is expelled through an outlet valve (not shown) of the pump head, which opens at a pre-determined pressure.
  • an outlet valve (not shown) of the pump head
  • the fuel pressure acting on the valve member 28 drops and the biasing spring 70 causes the valve member 28 to move back into its open position, as shown in Figure 1 , to admit fuel into the pumping chamber 16 once more.
  • the spring collar functions as a lift collar with which the armature engages to carry the valve member into its closed position.
  • separate spring and lift collars may be provided.
  • an inlet valve assembly for a high-pressure fuel pump may comprise an inlet valve member moveable between open and closed positions to control the fuel flow from a source of low-pressure fuel to a pumping chamber of the fuel pump, and an electromagnetic actuator comprising a core member, a solenoid coil, and an armature moveable towards the core member in response to energisation of the coil.
  • the armature In a first phase of operation, the armature is decoupled from the valve member to allow movement of the armature towards the core member without movement of the valve member, and in a second phase of operation, the armature is coupled to the valve member to carry the valve member towards its closed position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Magnetically Actuated Valves (AREA)

Claims (13)

  1. Einlassventilanordnung (14) für eine Hochdruckkraftstoffpumpe, die aufweist:
    ein Einlassventilelement (28), das zwischen offenen und geschlossenen Positionen bewegbar ist, um den Kraftstofffluss von einer Quelle (24) eines Kraftstoffs mit niedrigem Druck zu einer Pumpenkammer (16) der Kraftstoffpumpe zu steuern; und
    einen elektromagnetischen Aktuator (50), der ein Kernelement (52), eine Solenoidspule (54) und einen Anker (58) aufweist, der bewegbar ist in Richtung des Kernelements (52) in Reaktion auf eine Bestromung der Spule (54);
    dadurch gekennzeichnet, dass in einer ersten Betriebsphase der Anker (58) von dem Ventilelement (28) entkoppelt ist, um eine Bewegung des Ankers (58) in Richtung des Kernelements (52) ohne einer Bewegung des Ventilelements (28) zu ermöglichen, und wobei in einer zweiten Betriebsphase der Anker (58) mit dem Ventilelement (28) gekoppelt ist, um das Ventilelement (28) in Richtung seiner geschlossenen Position zu tragen, und wobei
    das Ventilelement (28) einen Hebekragen (72) trägt, wobei der Anker (58) ausgebildet ist zum Kontaktieren des Hebekragens (72), um den Anker (58) mit dem Ventilelement (28) in der zweiten Betriebsphase zu koppeln,
    die Einlassventilanordnung weiter eine Biasfeder (70) aufweist, um das Ventilelement (28) in seine offene Position zu bringen, und wobei der Hebekragen (72) einen Federsitz für die Biasfeder (72a) aufweist.
  2. Eine Einlassventilanordnung gemäß Anspruch 1, wobei ein ringförmiger Zwischenraum (75) zwischen dem Anker (58) und dem Ventilelement (28) definiert ist.
  3. Eine Einlassventilanordnung gemäß Anspruch 2, wobei der Anker (58) im Allgemeinen rohrförmig ist und wobei der ringförmige Zwischenraum (75) teilweise durch einen inneren Kragen (58c) des Ankers (58) definiert ist.
  4. Eine Einlassventilanordnung gemäß einem der vorhergehenden Ansprüche, wobei der Hebekragen (72) eingepresst oder an das Ventilelement (28) gecrimpt ist.
  5. Eine Einlassventilanordnung gemäß nach einem vorhergehenden Anspruch, die weiter Anschlagmittel (74, 76) aufweist zum Begrenzen der Öffnungsbewegung des Ventilelements (28).
  6. Eine Einlassventilanordnung gemäß Anspruch 5, wobei das Anschlagmittel ein Anschlagelement (74) aufweist, das an dem Ventilelement (28) getragen wird und ausgebildet ist, um gegen einen Gehäuseteil (76) der Kraftstoffpumpe zu stoppen, um die Öffnungsbewegung des Ventilelements (28) zu begrenzen.
  7. Eine Einlassventilanordnung gemäß Anspruch 6, wobei das Anschlagelement (74) zwischen dem Anker (58) und dem Ventilelement (28) angeordnet ist, und wobei das Anschlagelement (74) aus einem nichtmagnetischen Material besteht.
  8. Eine Einlassventilanordnung gemäß Anspruch 6 oder Anspruch 7, wobei das Anschlagelement (74) eine rohrförmige Hülse aufweist.
  9. Eine Einlassventilanordnung gemäß einem der Ansprüche 5 bis 8, wobei das Anschlagelement (74) eine Bewegung des Ankers (58) weg von dem Kernelement (52) begrenzt.
  10. Eine Einlassventilanordnung gemäß einem vorhergehenden Anspruch, die weiter ein nichtmagnetisches Abstandselement (78) aufweist, das zwischen dem Anker (58) und dem Kernelement (52) angeordnet ist.
  11. Eine Einlassventilanordnung gemäß einem vorhergehenden Anspruch, wobei das Kernelement (52) einen verlängerten Teil (52e) umfasst, der den Anker (58) entlang der Achse der Bewegung des Ankers (52) über zumindest einen Teil des Bewegungsbereichs des Ankers (52) überlappt.
  12. Eine Einlassventilanordnung gemäß Anspruch 11, wobei der verlängerte Teil (52e) den Anker (58) entlang der Achse der Bewegung des Ankers (52) über den gesamten Bewegungsbereichs des Ankers (52) überlappt.
  13. Eine Einlassventilanordnung gemäß Anspruch 11 oder Anspruch 12, wobei der verlängerte Teil (52e) eine Aussparung (52d) definiert, die teilweise den Anker (52) aufnimmt.
EP12177133.1A 2012-07-19 2012-07-19 Ventilanordnung Active EP2687712B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP12177133.1A EP2687712B1 (de) 2012-07-19 2012-07-19 Ventilanordnung
HUE12177133A HUE025798T2 (en) 2012-07-19 2012-07-19 valve Layout

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EP12177133.1A EP2687712B1 (de) 2012-07-19 2012-07-19 Ventilanordnung

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Publication number Priority date Publication date Assignee Title
DE102014220975A1 (de) * 2014-10-16 2016-04-21 Robert Bosch Gmbh Elektromagnetisch betätigbares Einlassventil und Hochdruckpumpe mit Einlassventil
GB201502693D0 (en) * 2015-02-18 2015-04-01 Delphi International Operations Luxembourg S.�.R.L. Actuator assembly of a digital inlet valve
DE102015220387A1 (de) * 2015-10-20 2017-05-04 Robert Bosch Gmbh Ankerbaugruppe sowie elektromagnetisch betätigbares Ventil, insbesondere Saugventil
DE102015220383A1 (de) * 2015-10-20 2017-04-20 Robert Bosch Gmbh Elektromagnetisch betätigbares Saugventil für eine Hochdruckpumpe sowie Hochdruckpumpe
ITUB20156824A1 (it) * 2015-12-09 2017-06-09 Magneti Marelli Spa Pompa carburante alleggerita per un sistema di iniezione diretta e relativo metodo di montaggio
IT201600121614A1 (it) * 2016-11-30 2018-05-30 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
GB2561189A (en) * 2017-04-04 2018-10-10 Delphi Int Operations Luxembourg Sarl Piezo controlled inlet valve

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Publication number Priority date Publication date Assignee Title
JPS6231786A (ja) * 1985-07-31 1987-02-10 Diesel Kiki Co Ltd 電磁流体制御弁
US6056264A (en) * 1998-11-19 2000-05-02 Cummins Engine Company, Inc. Solenoid actuated flow control valve assembly
EP1921307B1 (de) 2006-11-08 2012-08-15 Delphi Technologies Holding S.à.r.l. Kraftstoffeinspritzsystem
US20080203347A1 (en) * 2007-02-28 2008-08-28 Santos Burrola Control valve for a gas direct injection fuel system
DE102008018018A1 (de) 2008-04-09 2009-10-15 Continental Automotive Gmbh Pumpe zur Förderung eines Fluids
EP2138706B1 (de) * 2008-06-27 2010-11-10 C.R.F. Società Consortile per Azioni Kraftstoffeinspritzgerät mit symmetrischem Mess-Servoventil für einen Verbrennungsmotor

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HUE025798T2 (en) 2016-05-30

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