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
  • F04B1/0408—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
  • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam

Definitions

• the invention relates to a pump, in particular a high-pressure fuel pump of a fuel injection system, having the features of the preamble of claim 1.
• a high-pressure pump of a fuel injection system is known from DE 10 2006 012 458 AI.
• the pump has a pump cylinder, which in turn has a cylinder bore.
• a pump piston is arranged, which is translationally movable up and down and cooperates via a plunger assembly with a drive unit, wherein the pump piston is connected to a spring plate and rests against the plunger assembly.
• a sealing element between the pump piston and the cylinder bore is arranged and a plunger spring is supported via the spring plate in a plunger body of the plunger assembly.
• this pump is designed so that you can for example be used in a crankcase of an internal combustion engine and has no separate drive shaft.
• a plug-in pump for feeding high-density fuel into a high-pressure accumulator for supplying a combustion chamber of the internal combustion engine
• the plug-in pump comprises a housing with the pump working space, which is connected by a suction line to the suction valve and by a high pressure line with a high pressure valve is.
• the plug-in pump can be used in particular in the crankcase of the internal combustion engine and is described for example in DE 10 2008 041 383 AI.
• the pump according to the invention with the features of claim 1 has the advantage that a larger contact surface between the components is obtained by means of the design of a double salmon of a guide pin, which is supported in a guide groove of a plunger body.
• the stresses in both components, in particular in the region of the two-flute and the guide groove are lower, since a force from a rotational momentum can be distributed over the larger contact surface, in particular in comparison with the prior art, in which both components have a punctiform and thus have small contact surface.
• Due to the larger contact surface due to the design of the two-salmon heat generation is also reduced due to friction between the components, since the force can be distributed over a larger contact area and thus the
• Heat development can be reduced.
• the lower heat generated by friction in the component guide pin also results in the inventive design of the pump because a better cooling can be done by a flowing lubricant because the guide pin has a larger diameter compared to the guide pin of the prior art and there by the formation of the double salmon increases the surface area of the component compared to the prior art. Thereby, the probability of failure of a rotation can be reduced, whereby the life of the entire pump can be increased.
• a connection of the guide pin is formed with a receptacle in a guide by means of a clearance fit.
• connection guide pin and guide according to claim 2 has the advantage that the rotation has an increased life, since at a rotation of the plunger body of the two-leaf of the guide pin and the guide groove of the plunger body can form a more uniform contact surface.
• the guide pin is thereby secured against being moved out of the receptacle that a locking pin and / or a locking screw engages in the guide pin.
• a complexity of the connection guide pin and recording in the guide can be improved because the guide pin now no longer, as is necessary in the prior art, must be pressed by means of a press fit into the receptacle to the guide pin against falling out to secure.
• the interference fit described in the prior art requires a complex processing of an outer diameter of the guide pin and an inner diameter of the receptacle.
• the outer diameter of the guide pin and the inner diameter of the receptacle must be measured prior to pressing the guide pin into the receptacle before each assembly with respect to deviations of the tolerance pairings in order to ensure the optimum interference fit.
• the advantage of the inventive design of the pump according to claims 3 and 4 offers the advantage that this complex and costly processing step of the components guide pin and recording can be omitted, as well as the complex and costly measurement of deviations before mounting the two components.
• the machining and assembling time can be reduced, and thus the machining cost and the assembling cost can be reduced.
• the two-flat in the direction of a longitudinal axis in the contact region with the guide groove may have a width crowning.
• the components form only a small contact area. Due to the low torque and the low power but despite the small contact area no high voltages in the components and it ensteht only a low frictional heat.
• flank line of the two-plaice deforms elastically, due to the force acting perpendicularly on the flank line and the width crowning of the flank line is reduced. As a result, the flank line of the double salmon and the guide groove of the tappet
• Two salmon have the advantage that a high contact torque between the component guide pin and ram body is created with a high twisting moment and thus the stress load, in particular the surface tension, in the components can be reduced. This allows a longer service life of the two components ram body and guide pin, which form the rotation, and thus the probability of failure of the entire pump is reduced.
• a heat treatment and / or coating of the two friction partners offers the advantage that the wear of the double salmon of the guide pin and the guide groove in the tappet body is minimized, thereby increasing the service life and reducing the probability of failure of the two elements.
• a material removal of both friction partners is reduced and thus damage to the surrounding elements, which may be flushed with a medium, which in particular can be fuel and / or oil, are reduced by abrasive particles.
• claim 9 and 10 can be achieved by a targeted lubrication and thus a reduction of a friction coefficient of the friction partner two times the guide pin and guide groove in the plunger body, in particular by a friction-reducing medium, the advantage that the heat energy occurring is reduced.
• a friction-reducing medium By reducing the heat energy on the one hand damage to the surrounding components is reduced, and on the other hand, the aging of the surrounding medium is reduced because the medium is not heated as much. This can increase the life of the pump and the life of an internal combustion engine.
• the inventive design of the pump according to claims 9 and 10 ensures that the friction partners, in particular by the feeding and the discharge of a medium, are cooled and thus the wear is reduced by heat.
• a pump according to the invention in a perspective view, a designated in Figure 1 with II section of the pump in an enlarged view with a plunger body and an adjacent guide, a designated in Figure 2 with AA section of the plunger body and the adjacent guide, one in Figure 2 with III designated section of the pump in an enlarged view with the guide, a safety pin and a guide pin, a designated in Figure 2 with III section of the pump in an enlarged view with the guide, a safety screw and the guide pin, one in Figure 2 with BB designated plan view of a two-leaf of a guide pin
• Fig. 1 shows a perspective view of a pump 1, which is designed as a high-pressure fuel pump and is preferably installed in a common-rail injection system and which in particular has a suction valve 2.
• a pump 1 fuel supplied from a low-pressure fuel system which has at least one tank, a filter and a low-pressure pump is delivered via a high-pressure port 7 into a high-pressure accumulator, from which the fuel stored there is taken from fuel injectors for injection into assigned combustion chambers of an internal combustion engine.
• the region of a plunger assembly 9 can be seen, which cooperates with a drive unit, not shown, which in particular via a camshaft 5, as shown in Fig. 2, which has the plunger assembly 9 and thus a connected thereto pump piston 13th placed in a translational up and down movement.
• the pump 1 has a cylinder head assembly 3 and the
• FIG. 2 shows a sectional view section of the pump 1 in an enlarged
• the pump 1 has the plunger assembly 9, which in turn has the plunger body 21 and a roller 25.
• a further aspect of the pump 1 is that a longitudinal axis 8 of the plunger body 21 and an axis of rotation 10 of the camshaft 5 are arranged perpendicular to one another, wherein the longitudinal axis 8 of the plunger body 21 in the direction of a translational up and down movement of the plunger body 21 and thus the plunger Assembly 9 runs during pump operation.
• the camshaft 5 also has a cam 11, the cam 11 is in contact with the roller 25 of the plunger assembly 9.
• the guide 24 also has a receptacle 6, in particular as a recess and / or bore perpendicular to the longitudinal axis. 8 in the guide 24 runs.
• a guide pin 4 is inserted in the direction of Einschiebeachse 26 which projects into an inner diameter and thus the cylinder bore 29 of the guide 24.
• the guide pin 4 On the side on which the guide pin 4 protrudes into the cylinder bore 29 of the guide 24, the guide pin 4 at the end in the direction of Einschiebeachse 26, a two-flat 17, wherein the insertion axis 26 is parallel to the axis of rotation 10.
• the insertion axis 26 extends in the direction in which the guide pin 4, in particular by means of a clearance fit 12, is inserted into the receptacle 6 of the guide 24.
• this two-fold 17 of the guide pin 4 protrudes into a guide groove 18 of the plunger body 21.
• the guide 24 may be located, for example, in a pump housing or in a crankcase of the internal combustion engine.
• the guide groove 18 is formed in particular as a longitudinal groove which extends parallel to the longitudinal axis 8 of the plunger assembly 9.
• the entire plunger assembly 9 can translate upward and downward in the direction of the longitudinal axis 8 during operation of the pump 1.
• section A-A shown in Fig. 3 of FIG. 2 is shown in plan view, as the two-flat 17 of the guide pin 4 is guided in the guide groove 18 and wherein rotation of the plunger body 21 about the longitudinal axis 8 is prevented.
• the two-flat 17 has a heat-treated and / or coated contact region 20.
• the plunger body 21 also has a heat-treated and / or coated running region 22, in particular in the region in which the guide groove 18 is in contact with the two-flats 17 of the guide pin 4.
• the two friction partners in the contact area can be lubricated or cooled specifically, in particular by supplying and discharging a medium, which is in particular oil.
• a medium which is in particular oil.
• the friction partners Zweiflach 17 and guide groove 18 can be cooled and thus the wear is reduced by heat development in the components.
• the guide pin 4 is secured by a locking pin 14 and / or by a locking screw 16 against falling out of the receptacle 6 in the guide 24.
• the locking pin 14 and / or the locking screw 16 are pressed in the direction of the longitudinal axis 8 in the guide 24 and / or screwed.
• the guide pin 4 is inserted with a clearance fit 12 in the receptacle 6 of the guide 24, whereby the guide pin 4 can better adapt to the dynamic movements of the plunger body 21. Due to the clearance 12, the guide pin 4 can partially adapt to the movements of the plunger body 21 during a highly dynamic pump operation without the guide pin 4 becoming loose and falling out of the receptacle 6.
• Fig. 4 shows a section of the pump 1 in an enlarged view with the guide 24, a securing pin 14 and the guide pin 4.
• the securing pin 14 in the guide 24 in particular in the direction of
• the securing pin 14 is held by the press-fitting non-positively in the guide 24 and is thus secured against being moved out of the guide 24.
• the securing pin 14 engages with its guide pin 4 facing the end 23 in a recess 28 of the guide pin 4 and thereby fixed the guide pin 4 positively in the direction of Einschiebeachse 26 on a move out of the receptacle 6.
• This fixation of the guide pin 4 by means of Securing pin 14 is necessary because the guide pin 4 is by means of the clearance fit 12 in the receptacle 6 of the guide 24 and the guide pin 4 could move out of the receptacle 6 in pump operation in the direction of the axis of rotation 10.
• Fig. 5 shows a section of the pump 1 in an enlarged view with the guide 24, a locking screw 16 and the guide pin 4.
• the guide pin 4 is fixed in the direction of Einschiebeachse 26 by the Securing screw 16 engages with the guide pin 4 facing the end 23 in a recess 28 of the guide pin 4.
• the guide pin 4 is positively fixed in the direction of the insertion axis 26 and prevented from moving out of the receptacle 6.
• the securing screw 16 is used in Fig. 5, which is screwed into a thread 27 of the guide 24 in the direction of the longitudinal axis 8.
• the fixation of the guide pin 4 by means of the screwed-in locking screw 16 has the advantage that the connection can be solved easily by unscrewing the locking screw 16 and thus the guide pin 4 as needed dismantle. This offers advantages in maintenance.
• Fig. 6 is a designated in Fig. 2 with B-B plan view of the two-plane
• flank line 15 of the two salmon 17, which runs parallel to the longitudinal axis 8 and, as already shown, with the guide groove 18 of the plunger body 21 is in contact, and preferably has a symmetrical crown. As shown in FIG. 6, this symmetrical crowning may be present on two flank lines 15 of the contact surfaces of the two-flesh 17, which coincide with the guide groove
• the flank line 15 of the two-flat 17 in the direction of the longitudinal axis 8 at the height of Einschiebeachse 26 has the greatest thickness and / or crown.
• the flank line 15 is designed such that this greatest thickness and / or crown decreases in both directions away from the insertion axis 26 in the direction of the longitudinal axis 8 and thus takes place a return to the sides of the flank line 15.
• the two-plane 17 forms with the guide groove 18 of the plunger body 21 only a small line of contact. Due to the low torsional forces from the plunger body 21, however, the voltages in the two-plane 17 are not unacceptably high despite the small contact surface. As soon as the twisting forces from the plunger body 21 increase due to an increased torsional momentum, the flank lines 15 deform due to the elasticity of the material of the two-plaice and the crowning, which is preferably symmetrical, decreases. As a result, the two-plane 17 forms a larger contact surface with the guide groove 18 of the tappet body, as a result of which the
• the two-flat 17 thus optimally adapts to the respective load situation on account of the preferred symmetrical crowning while the stresses in the two-plane 17 and thus in the component guide pin 4 remain low.

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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)

Priority Applications (1)

Applications Claiming Priority (2)

Publications (1)

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ID=60143687

Family Applications (1)

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Citations (7)

Family Cites Families (7)

• 2016
  • 2016-12-13 DE DE102016224835.9A patent/DE102016224835A1/de active Pending
• 2017
  • 2017-10-09 WO PCT/EP2017/075585 patent/WO2018108350A1/de active Application Filing
  • 2017-10-09 CN CN201780077075.1A patent/CN110062845B/zh active Active

Patent Citations (7)

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