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
  • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
  • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
  • F02M59/102—Mechanical drive, e.g. tappets or cams

Definitions

• the invention relates to a high-pressure pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
• Such a high-pressure pump is known from DE 199 07 311 Al.
• This high-pressure pump has a pump housing and at least one pump element arranged in the pump element.
• the pump element has a driven by a drive shaft of the high pressure pump in a stroke pump piston.
• the pump piston is tightly guided in a cylinder bore of a Pumpengehauseteils the high-pressure pump and limited in the cylinder bore a pump working space.
• the pump piston is supported at least indirectly via a hollow cylinder-shaped plunger on the drive shaft.
• the plunger is slidably guided in a bore of a Pumpengehauseteils in the direction of the longitudinal axis of the pump piston.
• the inventive high-pressure pump with the features of claim 1 has the advantage that an anti-rotation of the shock ice is ensured by simple means.
• the ball is a standard part that can be purchased inexpensively as a vendor.
• Embodiments and developments of the inventive high-pressure pump specified Due to the design according to claim 2, a low friction in the rotation of the shock ice is achieved because there is at least at a Abstutzung the ball on the plunger rolling friction. Due to the design according to claim 3, a safe investment of the ball is achieved in the groove of the shock ice. The embodiment according to claim 4, a particularly low friction is achieved because both between the ball and the plunger and between the ball and the recording
• FIG. 1 shows a high pressure pump for a fuel injector
• Figure 2 Internal combustion engine in a longitudinal section, Figure 2 is a designated II in Figure 1 section of the high-pressure pump in an enlarged view according to a first exemplary embodiment, Figure 3, the high-pressure pump in a section along line III-III in Figure 2, Figure 4 a in Figure 3 with IV designated Detail in again enlarged view and Figure 5 shows the detail II of the high-pressure pump according to a second exemplary embodiment.
• FIGS. 1 to 5 show a high-pressure pump for a fuel injection device of an internal combustion engine.
• the high-pressure pump has a multipart pump housing 10 in which a drive shaft 12 driven in rotation by the internal combustion engine is arranged.
• the drive shaft 12 is rotatably supported, for example, via two bearing points spaced apart from one another in the direction of the axis of rotation 13 of the drive shaft 12.
• the bearings can be arranged in different parts of the Pumpengehauses 10, for example, a first bearing point in a Grundkorper 14 of Pumpengehauses 10 and a second bearing point can be arranged in a connected to the base body 14 flange 15.
• the drive shaft 12 at least one cam 16 or eccentrically to its axis of rotation 13 formed portion, wherein the cam 16 may be formed as a multiple cam.
• the high pressure pump has at least one or more arranged in the housing 10 pump elements 18, each with a pump piston 20 which is driven by the cam 16 of the drive shaft 12 in a lifting movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12.
• a pump housing part 22 connected to the basic body 14 is provided, which is designed as a cylinder head.
• the pump housing part 22 has a voltage applied to an outer side of the base body 14 flange 24 and a through an opening in the base body 14 to the drive shaft 12 through protruding, at least approximately cylindrical projection 26 with respect to the flange 24 of smaller diameter.
• the pump piston 20 is tightly slidably guided in a formed in the neck 26 cylinder bore 28 in the pump housing part 22 and limited with its drive shaft 12 facing away from the end face in the cylinder bore 28 a pump working space 30.
• the cylinder bore 28 may extend into the flange 24, in the then the pump working space 30 is arranged.
• the pump chamber 30 has a in the
• Pump housing 10 extending fuel inlet channel 32 connects to a fuel inlet, for example, a Forderpumpe.
• a fuel inlet for example, a Forderpumpe.
• an inlet valve 34 opening into the pump working chamber 30 is arranged.
• the pump working chamber 30 also has a connection in the pump housing 10 extending fuel drain passage 36 with an outlet, which is connected for example to a high-pressure accumulator 110.
• One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine.
• an outlet valve 38 opening out of the pump working chamber 30 is arranged.
• a plunger 40 is arranged, via which the pump piston 20 is supported at least indirectly on the cam 16 of the drive shaft 12.
• the plunger 40 is hollow cylinder-shaped with a round outer cross-section and is slidably guided in a bore 42 of the base body 14 of the Pumpengehauses 10 in the direction of the longitudinal axis 21 of the pump piston 20.
• the longitudinal axis 41 of the shock ice 40 is thus at least substantially identical to the longitudinal axis 21 of the pump piston 20.
• a support member 44 is inserted in the drive shaft 12 facing end portion in which a roller 46 is rotatably mounted, which rolls on the cam 16 of the drive shaft 12.
• the axis of rotation 47 of the roller 46 is at least approximately parallel to the axis of rotation 13 of the drive shaft 12.
• the support element 44 has on its side facing the drive shaft 12 a recess 48 in which the roller 46 is mounted.
• the pump piston 20 may be coupled to the plunger 40, at least in the direction of its longitudinal axis 21. Alternatively, the pump piston 20 may not be connected to the plunger 40, in which case by the return spring 52, the system of the pump piston 20 is secured to the plunger 40. It can be provided that the return spring 52, for example via a spring plate 53 at a in the
• Diameter enlarged piston foot of the pump piston 20 engages, which is thereby held in abutment on a ram 40 of the jacket inwardly projecting flange, which in turn is held in contact with the support member 44, so that the entire composite of pump piston 20, ram 40 and support element 44 is acted upon with roller 46 to the cam 16 of the drive shaft 12 out.
• groove 56 In the outer casing of the impact ice 40 at least one extending in the direction of the longitudinal axis 41 groove 56 is arranged, which preferably at least in cross section is formed approximately nikabroughformig. In the groove 56 engages at least approximately radially to the longitudinal axis 41 of the baffle 40, a ball 58 with a part of its circumference, which is fixed in the pump housing 10 in the tangential direction to the plunger 40.
• Figures 2 to 4 is the
• High-pressure pump according to a first exemplary embodiment shown, in which the ball 58 is guided in a receptacle 60 in the direction of the longitudinal axis 41 of the bumper 40 movable.
• the receptacle 60 has, as shown in Figures 2 and 4, a trough-shaped recess 62 which is at least substantially prismatic in cross-section perpendicular to the longitudinal axis 41 of the baffle 40 and two opposing inclined walls, on which the ball 58 is applied in each case.
• the ball 58 dives with a part of its circumference in the recess 62 and is thereby fixed in the tangential direction of the shock ice 40, so that the plunger 40 is secured by the ball 58 against rotation about its longitudinal axis 41.
• the ball 58 rolls both in the groove 56 of the shock ice 40 and in the
• the receptacle 60 is as shown in Figures 2 and 3, for example, in a at least approximately radially arranged with respect to the longitudinal axis 41 of the baffle 40 arranged bore 64 in the base body 14 of the pump housing 10.
• the receptacle 60 is cylindrical in shape, on the tappet 40 facing the inside of the recess 62 is formed.
• the bore 64 is closed to the outside of the main body 14 of the Pumpengehauses 10 by means of a plug 66.
• a prestressed spring 68 between the plug 66 and the receptacle 60 is preferably a prestressed spring 68, for example a helical compression spring, clamped by the displaceable in the bore 64 receptacle 60 and thus the ball 58th is pressed towards the plunger 40.
• an elastic sealing ring 70 for example an O-ring, may be arranged to seal the interior of the pump housing 10 to the outside. It can be provided that the plug 66 is screwed or pressed into the bore 64. In addition, it can be provided that the flange part 15 at least partially covers the bore 64 in a state assembled with the basic body 14 and thus secures the stopper 66 in the bore 64.
• the receptacle 60 with the ball 58, the plug 66 and the spring 68 are inserted before the assembly of the Pumpengehauses 10 in the bore 64 from the outside of the base body 14 forth. When mounting the receptacle 60, it must be ensured that its recess 62 is aligned exactly parallel to the groove 56 of the baffle 40 in order to allow the lifting movement of the baffle 40 with the least possible friction.
• the depth of the groove 56 in the plunger 40 and thus the immersion depth of the ball 58 in the groove 56 and the bias of the spring 68 determine the size of the torque against which the plunger 40 can be secured against rotation.
• the high-pressure pump according to a second exemplary embodiment is shown, in which the basic structure of the high-pressure pump is the same as in the first exemplary embodiment, but the receptacle 160 is modified for the ball 58.
• the receptacle 160 has on its side facing the plunger 40 a kugelkalottenformige depression 162 in which the ball 58 is rotatably mounted.
• the receptacle 160 is in a blind bore of the Hole 64 in the base body 14 of the pump housing 10 occlusive stopper 166 slidably inserted. Between the plug 166 and the receptacle 160, the prestressed spring 68 is arranged.
• Exemplary embodiment is that the receptacle 160 is formed simpler than the first exemplary embodiment and that the receptacle 160 can be used in any rotational positions in the pump housing 10. However, in the second exemplary embodiment, only between the ball 58 and the plunger 40 rolling friction exists, while between the ball 58 and the receptacle 160 is sliding friction.

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Fuel-Injection Apparatus (AREA)

Applications Claiming Priority (2)

Publications (2)

Family

ID=37398784

Family Applications (1)

Country Status (4)

Families Citing this family (41)

Family Cites Families (3)

• 2005
  • 2005-09-29 DE DE102005046670A patent/DE102005046670A1/de not_active Withdrawn
• 2006
  • 2006-09-08 DE DE502006006407T patent/DE502006006407D1/de active Active
  • 2006-09-08 AT AT06793348T patent/ATE460584T1/de active
  • 2006-09-08 WO PCT/EP2006/066162 patent/WO2007036423A1/fr active Application Filing
  • 2006-09-08 EP EP06793348A patent/EP1931875B1/fr not_active Not-in-force

Non-Patent Citations (1)

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