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
• • 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
  • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
• • 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
  • F04B1/0439—Supporting or guiding means for the pistons

Definitions

• the present invention relates to a high pressure pump according to the preamble of claim 1 and a high pressure injection system according to the preamble of claim 12.
• a high-pressure pump permanently ensures the maintenance of the pressure in the
• High pressure accumulator of the common rail injection system can be driven, for example, by a camshaft of the internal combustion engine by means of a drive shaft.
• Rotary vane pump used, which are upstream of the high-pressure pump.
• the prefeed pump delivers the fuel from a fuel tank through a fuel line to the high pressure pump.
• piston pumps are used as high-pressure pumps.
• a drive shaft is mounted. Radially to pistons are arranged in a cylinder.
• a roller with a roller rolling surface On the drive shaft with at least one cam is a roller with a roller rolling surface, which is mounted in a roller shoe.
• the roller shoe is connected to the piston, so that the piston is forced to oscillate translational motion.
• a spring applies to the roller shoe a radially directed to the drive shaft force, so that the roller is in constant contact with the drive shaft.
• the roller stands with the roller rolling surface on a shaft rolling surface as the surface of the drive shaft with the at least one cam in contact with the drive shaft.
• the roller is mounted by means of a sliding bearing in the roller shoe. At the sliding bearing of the roller shoe occur deposits or occurs a deposit formation, z. B. due to cracked fuel with which the slide bearing is lubricated. The deposits cause the game or distance between the
• DE 10 2006 045 933 A1 shows a high-pressure pump for high-pressure fuel delivery.
• the high-pressure pump has a drive shaft with cams.
• Cylindrical rollers are supported by roller shoes and rest on the cams.
• the roller shoes are by means of a plunger assembly in a bore of a
• the pump elements are at the
• Inventive high-pressure pump in particular for a motor vehicle, for conveying a fluid, in particular fuel, for. B. diesel, comprising a drive shaft with at least one cam, at least one piston, at least one cylinder for supporting the at least one piston, a
• Roller shoe with a mounted in the roller shoe with a sliding bearing Roller and the piston indirectly with the roller shoe on the drive shaft with the at least one cam is supported, so that from the at least one piston a translational movement due to a rotational movement of the drive shaft executable, wherein the sliding bearing on the roller shoe outside an operating contact surface of the sliding bearing at least one
• Recess has. Due to the at least recess, no deposits or deposits can occur on the at least one recess, which can cause jamming of the roller in the roller shoe or an increase in the friction of the roller. This can advantageously in a low technical effort, a jamming of the roller in the
• the at least one recess is formed as at least one axial groove and preferably the roller shoe on two axial grooves and / or there is at the at least one recess, in particular the at least one axial groove, no contact between the roller and the roller shoe ,
• An axial groove on the roller shoe allows the clamping to be prevented over a larger area of the roller shoe in the direction of the axis of rotation of the roller.
• the at least one recess in particular the at least one axial groove, is formed in the tangential direction between the operating contact surface and an assembly aid of the plain bearing.
• the mounting aid is essentially required only that during the assembly of the high-pressure pump, the roller is fixed to the roller shoe and possibly used during operation of the
• the at least one recess in particular the at least one axial groove, interrupts the plain bearing in a tangential manner
• Slide bearing and / or the at least one axial groove is formed completely in the axial direction of a rotation axis of the roller on the roller shoe.
• the axial groove is completely continuous in the direction of
• Rotation axis of the roller formed on the roller shoe It is expedient for the at least one recess to have a spacing of at least 0.5, 1, 2, 3 or 5 mm between the roller shoe and the roller rolling surface of the roller.
• the mounting aid of the plain bearing in the direction of the translational movement of the roller shoe is at least partially formed between the axis of rotation of the roller and a side of the roller shoe in the direction of the drive shaft.
• the operating contact surface comprises an angular range in a fictitious plane perpendicular to the axis of rotation of the caster, each beginning at opposite angles on a fictitious half-line intersecting the location of the operating contact surface with a minimum distance to the piston and the axis of rotation of the caster of less than 80 ° , 60 °, 40 °, 30 °, 15 °,
• the rest of the sliding bearing of the roller shoe comprises only the
• Rotation axis of the roller and the sliding bearing of the roller shoe on the mounting aid larger than at the operating contact surface.
• Distance between the axis of rotation and the mounting aid to at least 1, 3, 5, 10, 20 or 30% greater than the distance between the axis of rotation and the operating contact surface.
• the sliding bearing in particular the operating contact surface, with a coating, in particular
• Carbon coating provided to reduce the friction between the roller and the plain bearing.
• the coating reduces the friction between the roller and the slide bearing on the operating contact surface and is also abrasion resistant, so that the high pressure pump in the long-term and long-term operation of the coating only a very small and
• the roller shoe is provided with at least one lubricating channel, which in the at least one recess,
• Lubrication channel can additionally fuel as a lubricant to the sliding bearing, in particular to the operating contact surface, are performed. Thereby, the temperature of the sliding bearing of the roller shoe is reduced due to the friction occurring because heat is dissipated by the fuel. This can advantageously the formation of deposits and deposits on the
• the at least one lubrication channel is designed in the direction of the translational movement of the roller shoe, and preferably the at least one lubrication channel terminates on one side of the roller shoe in the direction of the drive shaft.
• the roller shoe is inside one
• Lubricating space arranged with fuel and in a translational movement of the piston from a top dead center to a bottom dead center thereby flows fuel into the lubrication channel and is then through the
• Lubrication channel passed to the at least one recess, thereby substantially increasing the lubrication of the sliding bearing of the roller shoe with fuel.
• a sliding bearing between the
• the high-pressure pump comprises a lubricating space and fuel is conveyed through the lubricating space for lubricating the high-pressure pump and within the lubricating space the roller shoe with the roller and preferably the drive shaft and partially preferably the piston is arranged.
• an eccentric shaft is considered as a drive shaft with at least one cam.
• Inventive high-pressure injection system for an internal combustion engine in particular for a motor vehicle, comprising a high-pressure pump, a high-pressure rail, preferably a prefeed pump for conveying a
• High-pressure pump is designed as a high pressure pump described in this patent application.
• the high-pressure injection system has a
• the producible by the high-pressure pump pressure in the high-pressure rail is, for example, in the range of 1000 to 3000 bar z. B. for diesel engines or between 40 bar and 400 bar z. B. for gasoline engines.
• High-pressure injection system in particular for a motor vehicle, comprises a high-pressure injection system described in this patent application and / or a high-pressure pump described in this patent application.
• It 1 is a cross section of a high-pressure pump
• FIG. 2 shows a section A-A according to FIG. 1 of a roller with roller shoe and a drive shaft from the prior art
• FIG. 3 shows a section A-A of FIG. 1 of the roller with roller shoe in a first embodiment
• FIG. 4 shows a section A-A according to FIG. 1 of the roller with roller shoe in a second exemplary embodiment
• Fig. 5 is a perspective view of the roller shoe of FIG. 3 and
• Fig. 6 is a highly schematic view of a high-pressure injection system.
• Fig. 1 is a cross section of a high-pressure pump 1 for a
• High-pressure injection system 36 shown.
• the high-pressure pump 1 serves to fuel, z. As gasoline or diesel, to promote an internal combustion engine 39 under high pressure.
• the pressure which can be generated by the high-pressure pump 1 is, for example, in a range between 1000 and 3000 bar.
• Fig. 2 a known from the prior art roller shoe 9 is shown.
• the high-pressure pump 1 has a drive shaft 2 with two cams 3, which performs a rotational movement about a rotation axis 26.
• the axis of rotation 26 lies in the plane of the drawing of FIG. 1 and is perpendicular to the
• a piston 5 is mounted in a cylinder 6, which is formed by a housing 8.
• a working chamber 29 is bounded by the cylinder 6, the housing 8 and the piston 5.
• Into the working space 29 opens an inlet channel 22 with an inlet valve 19 and an outlet channel 24 with an outlet valve 20.
• the inlet valve 19, z. As a check valve, is designed such that only fuel in the Working space 29 can flow and the exhaust valve 20, z.
• Check valve is designed so that only fuel can flow out of the working chamber 29.
• the volume of the working chamber 29 is changed due to an oscillating stroke movement of the piston 5.
• the piston 5 is indirectly supported on the drive shaft 2 from.
• a roller shoe 9 is attached to a roller 10.
• the roller 10 can perform a rotational movement, the
• Rotation axis 25 lies in the plane of the drawing of FIG. 1 and is perpendicular to the plane of Fig. 2, 3 and 4.
• the drive shaft 2 with the at least one cam 3 has a shaft rolling surface 4 and the roller 10 has a roller
• roller tread 1 1 of the roller 10 rolls on the shaft rolling surface 4 of the drive shaft 2 with the two cams 3 at a contact surface 12 from.
• the roller shoe 9 is mounted in a roller shoe bearing formed by the housing 8 as a slide bearing 13.
• Fig. 2 a known from the prior art slide bearing 13 is shown.
• Rolling surface 4 of the drive shaft 2 is.
• the roller shoe 9 and the piston 5 thus carry out together an oscillating stroke movement.
• Fig. 6 is a highly schematic representation of the high-pressure injection system 36 is shown for a motor vehicle with a high-pressure rail 30 or a
• a prefeed pump 35 delivers fuel from one
• Pre-feed pump 35 are driven by the drive shaft 2.
• the drive shaft 2 is coupled to a crankshaft of the engine 39.
• the high pressure rail 30 serves - as already described - to inject the fuel into the combustion chamber of the internal combustion engine 39.
• the funded by the feed pump 35 fuel is through the fuel line 33 to the
• High-pressure pump 1 passed.
• the one not required by the high-pressure pump 1 Fuel is thereby through a fuel return line 34 back into the
• a metering unit 37 controls and / or regulates the quantity of fuel supplied to the high-pressure pump 1, so that the fuel return line 34 can be dispensed with in a further embodiment (not shown).
• a first embodiment of the roller shoe 9 is shown with the roller 10 for a high-pressure pump 1 according to the invention.
• the sliding bearing 13 of the roller shoe 9 comprises an operating contact surface 14 and an assembly aid 15. Only at the operating contact surface 14 is a
• Carbon coating 41 formed coating 40 is present.
• the roller shoe 9 is made of metal, for example steel, such as the roller 10.
• the sliding bearing 13 no carbon coating 41 on.
• Direction 18 of the sliding bearing 13 is incorporated between the operating contact surface 14 and the carbon coating 41 and the two mounting aids 15 a semi-circular in cross-section axial groove 17 in the roller shoe 9 made of steel.
• the two axial grooves 17 between the operating contact surface 14 and the two mounting aids 15 thus form a recess 16 on the sliding bearing 13, so that no contact between the roller shoe 9 and the roller 10 can occur at the two axial grooves 17.
• the roller shoe 9 leads to the roller 10 a
• roller shoe 9 To be able to hold roller shoe 9.
• the operating contact surface 14 and the sliding bearing 13 has in the section in Fig. 3, a point 38 with a minimum distance to the piston 5 and in the section in Fig. 3 is at the point 38 to a point, but due the extension of the roller shoe 9 and the roller 10 perpendicular to the plane of Fig. 3, the point 38 is a line or a straight line.
• a first leg of the angle ⁇ is a fictitious half-line 45, beginning with the axis of rotation 25 in the section in Fig. 3 and this
• Halfway also cuts the point 38.
• the two angles ß are limited in two opposite directions of the fictitious half-line 45.
• the two angles ß in Fig. 3 are about 30 °, so that a
• Angular range ⁇ of the operating contact surface 14 is approximately equal to 60 °. A sufficiently large angular range ⁇ of the operating contact surface 14 is required so that the running roller 9 is sufficiently supported by the operating contact surface 14 of the roller shoe 9 during normal operation.
• the roller shoe 9 On a lower side or a side 44 of the roller shoe 9 in the direction of the drive shaft 2, the roller shoe 9 has a total of four lubrication channels 42 (FIG. 5).
• Lubrication channels 42 begin at the side 44 and respectively end and guide into the two axial grooves 17. In each case two lubrication channels 42 open into each of the two axial grooves 17. In the oscillating translational movement of the roller shoe 9 within the lubricating space with fuel is characterized by the Lubrication channels 42 led to the axial grooves 17 fuel and thereby the operating contact surface 14 is surrounded with additional fuel or
• Embodiment of the roller shoe 9 be executed without the lubrication channels 42.
• Roller shoe 9 of FIG. 3 and 5 have significant advantages for the
• High pressure pump 1 In one known from the prior art Roller shoe 9 (Fig. 2), the slide bearing 13 on no axial grooves 17. This forms in a known from the prior art
• Roller shoe 9 also in this area a coating or a deposit, because in general on the operating contact surface 14 due to the constant contact between the roller 10 and the operating contact surface 14 generally no
• FIGS. 3 and 5 may form deposits or deposits essentially only on the assembly aid 15.
• the mounting aid 15 since it is not required in normal operation for the sliding bearing of the roller 10, formed with a significantly greater distance of the rotation axis 25 of the roller 9, so that between the roller 10 and the roller rolling surface 1 1 and of the
• Mounting aid 15 is a very large distance or a very big game and this distance and this game is chosen so constructive that even with unfavorable and larger deposits on the mounting aid 15 no
• roller shoe 9 excluded in the direction of the drive shaft 2.
• the axial grooves 17 thus prevent a relative movement of the roller 10 relative to the roller shoe 9 in the direction of the drive shaft second
• roller shoe 9 a second embodiment of the roller shoe 9 is shown.
• the two axial grooves 17 are formed in the section in Fig. 4 is substantially rectangular and not semicircular. Otherwise, the roller shoe 9 according to FIG. 4 corresponds to the first embodiment of the invention shown in FIGS. 3 and 5
• roller shoe 9 Overall, significant advantages are associated with the high-pressure pump 1 according to the invention.
• the two axial grooves 17 prevent as simple and inexpensive constructive feature a relative movement of the roller 10 relative to the roller shoe 9 in the direction of the drive shaft 2, thereby clamping the roller 10 can be prevented in the roller shoe 9, because between the two mounting aids 15 and the roller 10 constructively a large Distance and a big game exists.

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

Priority Applications (2)

Applications Claiming Priority (2)

Publications (1)

Family

ID=47557166

Family Applications (1)

Country Status (4)

Families Citing this family (3)

Citations (4)

Family Cites Families (7)

• 2012
  • 2012-01-31 DE DE201210201302 patent/DE102012201302A1/de not_active Withdrawn
• 2013
  • 2013-01-15 EP EP13700229.1A patent/EP2809943B1/de active Active
  • 2013-01-15 WO PCT/EP2013/050629 patent/WO2013113544A1/de active Application Filing
  • 2013-01-15 CN CN201380007030.9A patent/CN104081038B/zh active Active

Patent Citations (4)

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