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
  • 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
  • F02M59/442—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 means preventing fuel leakage around pump plunger, e.g. fluid barriers
• • 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
  • F04B1/0408—Pistons
• • 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
• • 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
• • 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
  • F04B1/0448—Sealing means, e.g. for shafts or housings
• • 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
  • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for

Definitions

• the invention relates to a high-pressure pump, in particular a fuel pump for fuel injection systems. Specifically, the invention relates to the field of high pressure pumps for fuel injection systems of air compressing, auto-igniting
• Fuel injection device of an internal combustion engine known.
• High-pressure pump has a pump housing, in which a pump element is arranged, which is driven by a drive shaft in a lifting movement
• Pump piston is supported via a hohizylinderformigen ram on the drive shaft, wherein the plunger is slidably guided in a bore of a portion of the pump housing in the direction of the longitudinal axis of the pump piston.
• a return spring is provided, which ensures a contact of the pump piston on the plunger, so that the entire composite of pump piston, plunger and support element is acted upon via a roller to the cam of the drive shaft.
• the known from DE 10 2005 046 670 A1 high pressure pump has the disadvantage that the return spring, which must be designed relatively strong, occupies a relatively large space in the pump housing. However, since the space is limited in principle, there are limitations on the performance of the high-pressure pump in terms of long-term load and speed capability.
• the high pressure pump according to the invention with the features of claim 1 has the advantage that a functionality of the high pressure pump is improved. Specifically, improved long-term durability and increase in speed capability can be achieved.
• the plunger body comprises a ram paragraph, wherein the
• a diameter of the plunger spring can be chosen to be large in relation to the available space in a bore of the pump housing.
• the length of a roller of the pump assembly can be set comparatively large.
• the plunger body has an inner guide portion and an outer guide portion, which are interconnected via the ram paragraph, and that the plunger body at its inner guide portion at the approach of the cylinder head and at its outer guide portion in the bore of the
• the inner guide section has at least one bore which extends from an outer side of the inner guide section to an inner side of the inner guide section.
• Tappet body are guided.
• Such a lubricant is advantageously formed by the medium to be delivered by the high-pressure pump when the high-pressure pump is used, for example, for delivering diesel oil.
• the approach has a cylinder bore in which a drivable by the drive shaft pump piston of the pump assembly is performed, that at one of the drive shaft end facing the approach, a seal between the neck and the pump piston is provided and that the seal over the bore in the inner guide portion of the plunger body is acted upon by a pressure of a lubricant.
• the sealing effect of the seal can be optimized. Because the seal then works self-reinforcing, since with increasing pressure of the lubricant during the delivery stroke and the sealing effect increases.
• the pump assembly has a roller shoe and a roller mounted on a bearing surface of the roller shoe, that the plunger spring acts on the roller via the plunger body and the roller shoe against a running surface of the cam, that the roller shoe is inserted into the outer guide portion of the plunger body and that the roller shoe has at least one lubricant bore, wherein the lubricant bore opens on the one hand into a gap which is bounded by the inside of the tappet body and an upper side of the roller shoe which faces away from the bearing surface, and the lubricant bore on the other hand into the bearing surface of the roller shoe empties.
• a pressure lubrication for the roller mounted in the roller shoe can be achieved via the lubricant bore.
• the outer guide portion of the plunger body receives a bearing pin on which a roller of the pump assembly is mounted, and that the plunger spring acts on the roller via the plunger body and the bearing pin against a running surface of the cam.
• the plunger body has a support surface which faces away from the roller, and that the pump piston is supported on the support surface.
• the bearing pin is preferably pressed into the plunger body. In this way, the plunger body can also take over the function of storage of the role. Here, the length of the roll can be set comparatively large.
• the plunger body has at least one lubricant bore, that the lubricant bore opens into a gap on the one hand, which is bounded by the inside of the plunger body and the support surface of the plunger body and that the lubricant bore on the other hand leads to the role.
• the seal between the neck and the pump piston can be acted upon with a pressure of a lubricant in the intermediate space, which can be guided into the intermediate space via the bore in the inner guide section or the lubricant bore.
• a bore in the inner guide portion of the plunger body can also be omitted.
• Fig. 1 is a high-pressure pump in a partial, axial sectional view
• Fig. 2 is a high pressure pump in a partial, axial sectional view
• Fig. 1 shows a high-pressure pump 1 in an excerpt, axial sectional view according to a first embodiment of the invention.
• the high-pressure pump 1 can be used in particular as a fuel pump for fuel injection systems
• a preferred use of the high pressure pump 1 is for a fuel injection system with a
• the high-pressure pump 1 has a pump housing 2, which may be configured in one or more parts. Furthermore, the high-pressure pump 1 has a cylinder head 3, which is connected to the pump housing 2. The pump housing 2 has a bore 4 into which a projection 5 of the cylinder head 3 extends. In the area of the bore 4, a pump assembly 6 of the high-pressure pump 1 is arranged.
• the high-pressure pump 1 also has a drive shaft 7 with a cam 8.
• the drive shaft 7 is mounted in a suitable manner in the pump housing. In operation, the drive shaft 7 rotates about an axis of rotation 9.
• the cam 8 can be a single or
• cam 8 may be formed.
• the term of the cam 8 also includes embodiments of the drive shaft 7, in which, for example, the cam 8 is formed by an eccentric to the axis of rotation 9 formed portion on the drive shaft 7.
• the drive shaft 7 is used to drive the pump assembly 6.
• the cam 8 of the pump assembly 6 is assigned.
• the cam 8 In this case, further correspondingly configured pump assemblies can be assigned, which are arranged angularly offset relative to the axis of rotation 9.
• the drive shaft 7 may also comprise further cams, which are associated with further pump assemblies. In this way, for example, a radial or
• Row piston pump 1 can be realized.
• the pump assembly 6 has a plunger body 10.
• the plunger body 10 comprises an inner guide portion 1 1, an outer guide portion 12 and a ram paragraph 13.
• the inner guide portion 1 1 and the outer guide portion 12 are connected to each other via the ram paragraph 13.
• the plunger body 10 has an outer side 14 and an inner side 15. Further, the plunger body 10 in this embodiment, bores 16, 17 which each extend from the outer side 14 of the inner guide portion 1 1 to the inner side 15 of the inner guide portion 1 1 of the plunger body 10.
• the pump assembly 6 also has a pump piston 18 which is guided in a cylinder bore 19.
• the cylinder bore 19 extends through the projection 5 of the cylinder head 3.
• the pump piston 18 is guided along an axis 20 of the pump assembly 6 in the cylinder bore 19.
• Pump piston 18 here limits a pump working space 22.
• the high-pressure pump 1 has an inlet valve 25 and an outlet valve 26. Fuel can be fed into the pump working chamber 22 via the inlet valve 25. The high pressure fuel can through the outlet valve 26 from the
• the pump assembly 6 has a roller shoe 27 and a roller 28, wherein the roller 28 is mounted on a bearing surface 29 of the roller shoe 27.
• the roller 28 abuts a running surface 30 of the cam 8.
• the roller 28 rolls on the running surface 30 of the cam 8, so that a stroke of the cam 8 via the roller 28 and the roller shoe 27 is transferred to the pump piston 18.
• the roller shoe 27 is inserted into the tappet body 10 in this embodiment.
• the roller shoe 27 is supported on the plunger paragraph 13 of the plunger body 10.
• a guide of the roller 28 along its axis of rotation 31 is given by the inner side 15 of the outer guide portion 12 of the plunger body 10.
• the pump piston 18 has a collar 32 which on an upper side 33 of the
• Roller shoe 27 rests.
• the top 33 is in this case facing away from the bearing surface 29.
• the driving element 35 has through holes 36, 37.
• the driving element 37 encloses the
• Carrier element 35 and the top 33 of the roller shoe 27 is held.
• the pump assembly 6 has a plunger spring 40.
• the plunger spring 40 is further away from the axis 20 than the inner guide portion 1 1 of
• the plunger body 10 is guided in this embodiment both on the projection 5 and in the bore 4 of the pump housing 2.
• the plunger body 10 is guided at its inner guide portion 1 1 at the neck 5.
• the inner side 15 of the inner guide portion 1 1 of the plunger body 10 is guided on an outer side 41 of the projection 5.
• the plunger spring 40 surrounds the inner guide portion 1 1 of the plunger body 10.
• the plunger spring 40 surrounds the plunger body 10 in this embodiment in sections, namely in the region of the inner guide portion 1 1.
• the plunger body 10 is guided in sections on the neck 5 of the cylinder head 3, namely with its inner guide portion 1 1.
• the plunger spring 40 may thus have a large diameter. Specifically, considering a required clearance, an outer diameter 42 of the lifter spring 40 can be made substantially as large as a bore diameter 43 of the bore 4 of the pump housing 2. Thus, the lifter spring 40 can be realized with a large spring constant. In addition, there is an improved
• the plunger spring 40 is supported on the one hand on the plunger paragraph 13. On the other hand, the plunger spring 40 is supported in this embodiment on an underside 44 of the plunger paragraph 13.
• transverse forces can be absorbed by the guidance of the tappet body 10 at its outer portion 12 in the bore 4.
• a comparatively large clearance between the outer guide portion 12 and the plunger body 10 is preferably specified.
• an interior space 50 in which the plunger spring 40 is arranged relieved.
• the lubricant can be guided out of the inner space 50 via the bores 16, 17 into an intermediate space 51.
• an intermediate space 51 within the intermediate space 51 in this case a communication via the through holes 36, 37 of the driving element 35 is ensured.
• the lubricant can be performed in this embodiment by trained in the roller shoe 27 lubricant bores 52, 53 to the bearing surface 29 of the roller shoe 27.
• the lubricant holes 52, 53 open on the one hand in the intermediate space 51, from the inner side 15 of the inner
• the follower spring 40 acts on the roller 28 via the tappet body 10 and the roller shoe 27 inserted into the tappet body 10 against the running surface 30 of the cam 8.
• an abutment of the roller is present 28 ensures on the tread 30.
• the driving element 35 in this case ensures the entrainment of the pump piston 18 against the direction 34 for performing a suction stroke, wherein the fuel on the
• Inlet valve 25 is guided into the pump working chamber 22.
• FIG. 2 shows a high-pressure pump 1 in an excerpted, axial sectional representation according to a second exemplary embodiment of the invention.
• Embodiment takes the outer guide portion 1 1 of the plunger body 10 on a bearing pin 60, on which the roller 28 of the pump assembly 6 is mounted.
• the bearing pin 60 is in this case preferably pressed on both sides in the outer guide portion 12 of the plunger body 10.
• the roller 28 is mounted on the bearing pin 60. Over the outer guide portion 12 in this case a bearing along the axis of rotation 31 of the roller 28 is ensured.
• the plunger spring 40 acts on the roller 28 via the
• the plunger body 10 has in this embodiment, a support surface 61 which is configured on an intermediate part 62 of the plunger body 10.
• the support surface 61 faces away from the roller 28.
• the pump piston 18 is supported with its collar 32 on the support surface 61 of the intermediate part 62.
• the intermediate part 62 of the tappet body 10 also has lubricant bores 63, 64, which open on the one hand into the intermediate space 51, wherein the intermediate space 51 is bounded by the inner side 15 of the tappet body 10 and the support surface 61 of the tappet body 10.
• the lubricant bores 63, 64 lead to the roller 28. In operation, therefore, lubricant can be guided from the side of the roller 28 into the intermediate space 51.
• the seal 66 is acted upon by a pressure of a lubricant in the intermediate space 51.
• For the seal 66 is also a
• Return line 67 is provided, which extends through the lug 5.
• the return line 57 opens into an inlet 68 for the inlet valve 25th
• the lifter spring 40 may extend almost to the roller 28.
• the plunger body 10 can be guided in the region of the roller 28 with a larger fit in the pump housing 2.
• the gap 7 can be adjusted by a suitable embodiment of the through holes 36, 37 so that the hub creates a slight overpressure and the seal 66 sees slight overpressure and the roller 28 is lubricated via the lubrication holes 63, 64.
• both a long plunger spring 40 and a large roll width for the roller 28 can be realized.
• the greater spring length of the plunger spring 40 allows high speeds of the high pressure pump 1.
• the invention is not limited to the described embodiments.

Landscapes

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

Applications Claiming Priority (2)

Publications (1)

Family

ID=47594758

Family Applications (1)

Country Status (5)

Families Citing this family (12)

Family Cites Families (6)

• 2012
  • 2012-03-19 DE DE102012204264A patent/DE102012204264A1/de not_active Withdrawn
• 2013
  • 2013-01-21 WO PCT/EP2013/051022 patent/WO2013139498A1/de active Application Filing
  • 2013-01-21 IN IN7218DEN2014 patent/IN2014DN07218A/en unknown
  • 2013-01-21 CN CN201380014595.XA patent/CN104204501A/zh active Pending
  • 2013-01-21 EP EP13700746.4A patent/EP2828516A1/de not_active Withdrawn

Non-Patent Citations (1)

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