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EP3194770B1 - Piston pump - Google Patents

Piston pump Download PDF

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Publication number
EP3194770B1
EP3194770B1 EP15736837.4A EP15736837A EP3194770B1 EP 3194770 B1 EP3194770 B1 EP 3194770B1 EP 15736837 A EP15736837 A EP 15736837A EP 3194770 B1 EP3194770 B1 EP 3194770B1
Authority
EP
European Patent Office
Prior art keywords
bearing eye
roller
bolt
bearing
reciprocating pump
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
EP15736837.4A
Other languages
German (de)
French (fr)
Other versions
EP3194770A1 (en
Inventor
Christian Graspeuntner
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Publication date
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Publication of EP3194770A1 publication Critical patent/EP3194770A1/en
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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
    • F02M59/02—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
    • F04B1/0413—Cams
    • F04B1/0417—Cams consisting of two or more cylindrical elements, e.g. rollers
    • 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
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/02—Elasticity

Definitions

  • the present invention relates to a piston pump with a roller tappet.
  • Such a piston pump is from the laid-open specification DE 10 2011 076 022 A1 known.
  • the known piston pump comprises a roller tappet and a pump piston operatively connected to the roller tappet, the roller tappet having a roller shoe, a roller and a bolt.
  • a first bearing eye and a second bearing eye are formed in the roller shoe, the bolt being mounted in the first bearing eye and in the second bearing eye and the roller being rotatably arranged on the bolt.
  • Other piston pumps are also from the DE 10 2007 006 320 A1 , DE 10 2010 030 498 A1 and DE 10 2010 063 363 A1 known, wherein in these piston pumps the bolt is mounted more resiliently in the first bearing eye than in the second bearing eye.
  • roller tappet of the known piston pump is exposed to thermal stresses when exposed to high temperatures, which can lead to a reduction in the service life, smoothness and efficiency of the piston pump.
  • the piston pump according to the invention has a roller tappet which is robust against temperature loads. The service life and the efficiency of the piston pump are therefore not reduced by the temperature loads, and the piston pump runs more smoothly.
  • the piston pump has a roller tappet and a pump piston that is operatively connected to the roller tappet.
  • the roller tappet comprises a roller shoe, a roller and a bolt.
  • a first bearing eye and a second bearing eye are formed in the roller shoe, the bolt being mounted in the first bearing eye and in the second bearing eye.
  • the roller is rotatably arranged on the bolt.
  • the bolt is mounted more elastically in the first bearing eye than in the second bearing eye.
  • a recess is formed in the first bearing eye, the recess being a continuous slot, so that the first bearing eye comprises two bearing legs that are separated from one another on one side.
  • the bolt and the roller shoe can expand in different lengths without inducing excessive stresses in the components.
  • the stresses on the components, especially under temperature loads, are thus greatly reduced, which increases the service life of the entire piston pump accordingly. This also increases the smoothness and efficiency of the piston pump.
  • the roller shoe is arranged in a tappet housing.
  • the roller tappet can thus align itself within the tappet housing; This prevents stresses occurring due to storage conditions.
  • the first bearing eye has a first width and the second bearing eye has a second width, the first width being smaller than the second width.
  • the connection between the first bearing eye and the bolt is less rigid than the connection between the second bearing eye and the bolt.
  • this also makes the first bearing eye itself less rigid than the second bearing eye. The elasticity in the connection between the second bearing eye and the bolt can thus compensate for any different length expansions of the bolt and roller shoe.
  • a recess is formed in the first bearing eye.
  • the recess reduces the rigidity of the first bearing eye and thus also the rigidity of the connection between the first bearing eye and the bolt. Different changes in length of the bolt and roller shoe can be compensated for.
  • the recess can also serve to integrate further functions, for example the supply of lubricant into the first bearing eye.
  • the recess is a reduction in the wall thickness of the first bearing eye.
  • the rigidity of the first bearing eye is reduced in a very simple way. Especially in the event that the roller shoe is manufactured using a casting process, this is a very cost-effective solution.
  • the first bearing eye can advantageously be expanded elastically. As a result, the recess leads to a comparatively large increase in the diameter of the first bearing eye as soon as there is contact pressure with the bolt.
  • the recess is a continuous slot, so that the first bearing eye comprises two bearing legs that are separated from one another on one side. Due to the continuous slot, the first bearing eye is no longer closed over its entire circumference. This leads to a very strong reduction in the rigidity of the first bearing eye. As a result, the different linear expansions of the roller shoe and the bolt can be compensated for, even with very large temperature gradients.
  • the bolt is clamped into the first bearing eye and pressed into the second bearing eye. This means that the surface pressure between the first bearing eye and bolt is significantly lower than the surface pressure between the second bearing eye and bolt. In the first bearing eye, the bolt can therefore move relative to the roller shoe when the piston pump is in operation.
  • a further recess is formed in the second bearing eye. This also makes the second bearing eye comparatively soft and both in the first bearing eye and in the second bearing eye different length expansions of the roller shoe and the bolt can be compensated for.
  • the further recess is advantageously a reduction in the wall thickness of the second bearing eye.
  • the rigidity of the second bearing eye is reduced in a very simple way. Especially in the event that the roller shoe is manufactured using a casting process, this is a very cost-effective solution.
  • the bolt is clamped in the first bearing eye and in the second bearing eye.
  • the bolt can move relative to the roller shoe both in the first bearing eye and in the second bearing eye and accordingly compensate for different thermal expansions of the roller shoe and the bolt.
  • the piston pump according to the invention is part of a fuel injection system.
  • High pressures and high temperatures prevail, especially in high-pressure pumps in fuel injection systems.
  • the roller tappet of a piston pump used as a high pressure pump is therefore exposed to heavy loads.
  • the reduction or avoidance of thermally induced stresses in the roller tappet consequently not only increases the service life of the piston pump, but with it also the service life of the entire fuel injection system.
  • Fig. 1 shows a piston pump 1 with a pump housing 20.
  • a camshaft 21, a roller tappet 2 and a pump piston 10 are arranged in the pump housing 20.
  • the roller tappet 2 comprises a tappet body 15, a roller shoe 3, a roller 4 and a bolt 5.
  • the roller shoe 3 is arranged in the tappet body 15; In alternative embodiments, the tappet body 15 and the roller shoe 3 can also be made in one piece.
  • the bolt 5 is mounted in the roller shoe 3.
  • a first bearing eye 6 with a first width b6 and a second bearing eye 7 with a second width b7 are formed in the roller shoe 3, in which the bolt 5 is mounted or pressed.
  • the roller 4 is rotatably mounted on the bolt 5.
  • a cam 22 formed on the camshaft 21 interacts with the roller 4, so that the roller 4 rolls on the cam 22 when the camshaft 21 rotates.
  • the roller shoe 3 is operatively connected to the pump piston 10.
  • a spring 25 biases the pump piston 10 against the roller shoe 3 with the interposition of a washer 26.
  • Fig. 2 shows the roller tappet 2 from Fig. 1 in a side view.
  • the side view shows the roller shoe 3, the roller 4, the bolt 5 and the first bearing eye 6.
  • a recess 8 is formed in the first bearing eye 6.
  • the recess 8 runs over the entire wall thickness of the first bearing eye 6 in the form of a continuous slot, so that the first bearing eye 6 is divided into a first bearing leg 6a and a second bearing leg 6b, the first bearing leg 6a being separated on one side from the second bearing leg 6b .
  • An inner surface 6c of the first bearing eye 6, into which the bolt 5 is clamped or pressed, is thus made comparatively highly elastic due to the recess 8.
  • a further recess can be formed in the second bearing eye.
  • Fig. 3 shows an exemplary roller tappet 2 in an advantageous development.
  • the recess in the bearing eye 6 is not formed continuously over the entire wall thickness of the bearing eye 6, but only leads to a local reduction in the wall thickness of the first bearing eye 6 in this area.
  • the inner surface 6c is designed to be elastically expandable, that is to say that the bearing eye 6 is designed to be comparatively soft in the region of the recess 8.
  • the functioning of the piston pump 1 is as follows:
  • the camshaft 21 is driven by a drive unit (not shown), for example by a toothed belt connected to an internal combustion engine.
  • the cam 22 executes a rotational movement and describes a cam path.
  • the roller tappet 2, which is operatively connected to the cam 22 via the roller 4, executes a translatory upward and downward movement in the pump housing 20 due to the cam track, the direction of movement being perpendicular to the axis of the camshaft 21.
  • the pump piston 10 also performs the upward and downward movement and thereby compresses a fluid on the side opposite the roller tappet 2 in a compression chamber (not shown).
  • the fuel of a fuel injection system in the piston pump 1 can be brought under high pressure in this way.
  • connection between the bolt 5 and the first bearing eye 6 is more elastic or softer than the connection between the bolt 5 and the second bearing eye 7 . Thermal stresses in the bolt 5 and in the roller shoe 3 are thereby reduced or even avoided.

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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)
  • Reciprocating Pumps (AREA)

Description

Die vorliegende Erfindung betrifft eine Kolbenpumpe mit einem Rollenstößel.The present invention relates to a piston pump with a roller tappet.

Stand der TechnikState of the art

Eine derartige Kolbenpumpe ist aus der Offenlegungsschrift DE 10 2011 076 022 A1 bekannt. Die bekannte Kolbenpumpe umfasst einen Rollenstößel und einen mit dem Rollenstößel wirkverbundenen Pumpkolben, wobei der Rollenstößel einen Rollenschuh, eine Laufrolle und einen Bolzen aufweist. Im Rollenschuh sind ein erstes Lagerauge und ein zweites Lagerauge ausgebildet, wobei der Bolzen im ersten Lagerauge und im zweiten Lagerauge gelagert ist und wobei die Laufrolle drehbar auf dem Bolzen angeordnet ist. Weitere Kolbenpumpen sind auch aus der DE 10 2007 006 320 A1 , DE 10 2010 030 498 A1 und DE 10 2010 063 363 A1 bekannt, wobei bei diesen Kolbenpumpen der Bolzen im ersten Lagerauge elastischer gelagert ist als im zweiten Lagerauge.Such a piston pump is from the laid-open specification DE 10 2011 076 022 A1 known. The known piston pump comprises a roller tappet and a pump piston operatively connected to the roller tappet, the roller tappet having a roller shoe, a roller and a bolt. A first bearing eye and a second bearing eye are formed in the roller shoe, the bolt being mounted in the first bearing eye and in the second bearing eye and the roller being rotatably arranged on the bolt. Other piston pumps are also from the DE 10 2007 006 320 A1 , DE 10 2010 030 498 A1 and DE 10 2010 063 363 A1 known, wherein in these piston pumps the bolt is mounted more resiliently in the first bearing eye than in the second bearing eye.

Der Rollenstößel der bekannten Kolbenpumpe ist bei Temperaturbelastungen thermischen Spannungen ausgesetzt, die zu einer Reduzierung der Lebensdauer, der Laufruhe und des Wirkungsgrads der Kolbenpumpe führen können.The roller tappet of the known piston pump is exposed to thermal stresses when exposed to high temperatures, which can lead to a reduction in the service life, smoothness and efficiency of the piston pump.

Offenbarung der ErfindungDisclosure of the invention

Demgegenüber weist die erfindungsgemäße Kolbenpumpe einen Rollenstößel auf, der robust gegenüber Temperaturbelastungen ist. Die Lebensdauer und der Wirkungsgrad der Kolbenpumpe werden somit durch die Temperaturbelastungen nicht reduziert, und eine höhere Laufruhe der Kolbenpumpe wird erreicht.In contrast, the piston pump according to the invention has a roller tappet which is robust against temperature loads. The service life and the efficiency of the piston pump are therefore not reduced by the temperature loads, and the piston pump runs more smoothly.

Dazu weist die Kolbenpumpe einen Rollenstößel und einen mit dem Rollenstößel wirkverbundenen Pumpkolben auf. Der Rollenstößel umfasst einen Rollenschuh, eine Laufrolle und einen Bolzen. Im Rollenschuh sind ein erstes Lagerauge und ein zweites Lagerauge ausgebildet, wobei der Bolzen im ersten Lagerauge und im zweiten Lagerauge gelagert ist. Die Laufrolle ist drehbar auf dem Bolzen angeordnet. Der Bolzen ist im ersten Lagerauge elastischer gelagert als im zweiten Lagerauge. Erfindungsgemäß ist in dem ersten Lagerauge eine Ausnehmung ausgebildet, wobei die Ausnehmung ein durchgängiger Schlitz ist, so dass das erste Lagerauge zwei einseitig voneinander getrennte Lagerschenkel umfasst. Aufgrund der vergleichsweise hohen Elastizität im ersten Lagerauge bzw. der vergleichsweise geringen Steifigkeit der Verbindung zwischen erstem Lagerauge und Bolzen können der Bolzen und der Rollenschuh unterschiedliche Längendehnungen ausführen, ohne dabei zu große Spannungen in den Bauteilen zu induzieren. Die Beanspruchungen der Bauteile, speziell unter Temperaturbelastungen, sind damit stark reduziert, womit sich entsprechend die Lebensdauer der gesamten Kolbenpumpe erhöht. Weiterhin werden dadurch die Laufruhe und der Wirkungsgrad der Kolbenpumpe erhöht.For this purpose, the piston pump has a roller tappet and a pump piston that is operatively connected to the roller tappet. The roller tappet comprises a roller shoe, a roller and a bolt. A first bearing eye and a second bearing eye are formed in the roller shoe, the bolt being mounted in the first bearing eye and in the second bearing eye. The roller is rotatably arranged on the bolt. The bolt is mounted more elastically in the first bearing eye than in the second bearing eye. According to the invention, a recess is formed in the first bearing eye, the recess being a continuous slot, so that the first bearing eye comprises two bearing legs that are separated from one another on one side. Due to the comparatively high elasticity in the first bearing eye and the comparatively low rigidity of the connection between the first bearing eye and the bolt, the bolt and the roller shoe can expand in different lengths without inducing excessive stresses in the components. The stresses on the components, especially under temperature loads, are thus greatly reduced, which increases the service life of the entire piston pump accordingly. This also increases the smoothness and efficiency of the piston pump.

In einer vorteilhaften Weiterbildung ist der Rollenschuh in einem Stößelgehäuse angeordnet. Dadurch können bei der Umwandlung der Rotationsbewegung der Laufrolle in eine Translationsbewegung des Pumpkolbens auftretende Toleranzen ausgeglichen werden. Der Rollenstößel kann sich somit innerhalb des Stößelgehäuses selbst ausrichten; aufgrund von Lagerungsbedingungen auftretende Spannungen werden dadurch verhindert.In an advantageous development, the roller shoe is arranged in a tappet housing. As a result, tolerances occurring during the conversion of the rotational movement of the roller into a translational movement of the pump piston can be compensated. The roller tappet can thus align itself within the tappet housing; This prevents stresses occurring due to storage conditions.

In einer vorteilhaften Ausführung der Erfindung weist das erste Lagerauge eine erste Breite und das zweite Lagerauge eine zweite Breite auf, wobei die erste Breite kleiner als die zweite Breite ist. Dadurch ist in einer kostengünstigen Ausführung die Verbindung zwischen erstem Lagerauge und Bolzen weniger steif ausgeführt als die Verbindung zwischen zweitem Lagerauge und Bolzen. Weiterhin ist dadurch auch das erste Lagerauge selbst weniger steif ausgeführt als das zweite Lagerauge. Die Elastizität in der Verbindung zwischen zweitem Lagerauge und Bolzen kann somit etwaige unterschiedliche Längenausdehnungen von Bolzen und Rollenschuh ausgleichen.In an advantageous embodiment of the invention, the first bearing eye has a first width and the second bearing eye has a second width, the first width being smaller than the second width. As a result, in a cost-effective design, the connection between the first bearing eye and the bolt is less rigid than the connection between the second bearing eye and the bolt. Furthermore, this also makes the first bearing eye itself less rigid than the second bearing eye. The elasticity in the connection between the second bearing eye and the bolt can thus compensate for any different length expansions of the bolt and roller shoe.

Erfindungsgemäß ist in dem ersten Lagerauge eine Ausnehmung ausgebildet. Durch die Ausnehmung wird die Steifigkeit des ersten Lagerauges und damit auch die Steifigkeit der Verbindung zwischen erstem Lagerauge und Bolzen reduziert. Unterschiedliche Längenänderungen von Bolzen und Rollenschuh können dadurch ausgeglichen werden. Die Ausnehmung kann zusätzlich der Integration weiterer Funktionen dienen, beispielsweise der Schmierstoffzufuhr in das erste Lagerauge.According to the invention, a recess is formed in the first bearing eye. The recess reduces the rigidity of the first bearing eye and thus also the rigidity of the connection between the first bearing eye and the bolt. Different changes in length of the bolt and roller shoe can be compensated for. The recess can also serve to integrate further functions, for example the supply of lubricant into the first bearing eye.

In einer vorteilhaften Ausführung ist die Ausnehmung eine Verringerung der Wandstärke des ersten Lagerauges. Dadurch wird die Steifigkeit des ersten Lagerauges auf sehr einfache Weise reduziert. Speziell für den Fall, dass der Rollenschuh im Gießverfahren hergestellt ist, ist dies eine sehr kostengünstige Lösung.In an advantageous embodiment, the recess is a reduction in the wall thickness of the first bearing eye. As a result, the rigidity of the first bearing eye is reduced in a very simple way. Especially in the event that the roller shoe is manufactured using a casting process, this is a very cost-effective solution.

Vorteilhafterweise ist das erste Lagerauge elastisch aufweitbar. Die Ausnehmung führt dadurch zu einer vergleichsweise starken Durchmessererhöhung des ersten Lagerauges, sobald ein Kontaktdruck zum Bolzen vorhanden ist.The first bearing eye can advantageously be expanded elastically. As a result, the recess leads to a comparatively large increase in the diameter of the first bearing eye as soon as there is contact pressure with the bolt.

Erfindungsgemäß ist die Ausnehmung ein durchgängiger Schlitz, so dass das erste Lagerauge zwei einseitig voneinander getrennte Lagerschenkel umfasst. Aufgrund des durchgängigen Schlitzes ist das erste Lagerauge nicht mehr über seinen gesamten Umfang geschlossen. Dies führt zu einer sehr starken Reduzierung der Steifigkeit des ersten Lagerauges. Dadurch können selbst bei sehr großen Temperaturgradienten die unterschiedlichen Längenausdehnungen von Rollenschuh und Bolzen ausgeglichen werden.According to the invention, the recess is a continuous slot, so that the first bearing eye comprises two bearing legs that are separated from one another on one side. Due to the continuous slot, the first bearing eye is no longer closed over its entire circumference. This leads to a very strong reduction in the rigidity of the first bearing eye. As a result, the different linear expansions of the roller shoe and the bolt can be compensated for, even with very large temperature gradients.

In vorteilhaften Ausführungen der Erfindung ist der Bolzen in das erste Lagerauge eingeklemmt und in das zweite Lagerauge eingepresst. Das bedeutet, dass die Flächenpressung zwischen erstem Lagerauge und Bolzen deutlich geringer ist als die Flächenpressung zwischen zweitem Lagerauge und Bolzen. Im ersten Lagerauge kann der Bolzen im Betrieb der Kolbenpumpe somit Relativverschiebungen zum Rollenschuh ausführen.In advantageous embodiments of the invention, the bolt is clamped into the first bearing eye and pressed into the second bearing eye. This means that the surface pressure between the first bearing eye and bolt is significantly lower than the surface pressure between the second bearing eye and bolt. In the first bearing eye, the bolt can therefore move relative to the roller shoe when the piston pump is in operation.

In einer vorteilhaften Weiterbildung ist in dem zweiten Lagerauge eine weitere Ausnehmung ausgebildet. Dadurch ist auch das zweite Lagerauge vergleichsweise weich ausgebildet und sowohl im ersten Lagerauge als auch im zweiten Lagerauge können unterschiedliche Längenausdehnungen von Rollenschuh und Bolzen ausgeglichen werden.In an advantageous development, a further recess is formed in the second bearing eye. This also makes the second bearing eye comparatively soft and both in the first bearing eye and in the second bearing eye different length expansions of the roller shoe and the bolt can be compensated for.

Vorteilhafterweise ist die weitere Ausnehmung eine Verringerung der Wandstärke des zweiten Lagerauges. Dadurch wird die Steifigkeit des zweiten Lagerauges auf sehr einfache Weise reduziert. Speziell für den Fall, dass der Rollenschuh im Gießverfahren hergestellt ist, ist dies eine sehr kostengünstige Lösung.The further recess is advantageously a reduction in the wall thickness of the second bearing eye. As a result, the rigidity of the second bearing eye is reduced in a very simple way. Especially in the event that the roller shoe is manufactured using a casting process, this is a very cost-effective solution.

In einer vorteilhaften Weiterbildung ist der Bolzen in das erste Lagerauge und in das zweite Lagerauge eingeklemmt. Dadurch ist sowohl im ersten Lagerauge als auch im zweiten Lagerauge nur noch eine vergleichsweise geringe Kontaktkraft zum Bolzen vorhanden. Der Bolzen kann sowohl im ersten Lagerauge als auch im zweiten Lagerauge Relativverschiebungen zum Rollenschuh ausführen und dementsprechend unterschiedliche thermische Ausdehnungen von Rollenschuh und Bolzen ausgleichen.In an advantageous development, the bolt is clamped in the first bearing eye and in the second bearing eye. As a result, there is only a comparatively low contact force with the bolt in the first bearing eye as well as in the second bearing eye. The bolt can move relative to the roller shoe both in the first bearing eye and in the second bearing eye and accordingly compensate for different thermal expansions of the roller shoe and the bolt.

In vorteilhaften Ausführungen ist die erfindungsgemäße Kolbenpumpe Bestandteil eines Kraftstoffeinspritzsystems. Speziell in Hochdruckpumpen von Kraftstoffeinspritzsystemen herrschen hohe Drücke und hohe Temperaturen. Der Rollenstößel einer als Hochdruckpumpe eingesetzten Kolbenpumpe ist demzufolge starken Beanspruchungen ausgesetzt. Die Reduzierung bzw. Vermeidung von thermisch induzierten Spannungen im Rollenstößel erhöht demzufolge nicht nur die Lebensdauer der Kolbenpumpe, sondern mit ihr auch die Lebensdauer des gesamten Kraftstoffeinspritzsystems.In advantageous embodiments, the piston pump according to the invention is part of a fuel injection system. High pressures and high temperatures prevail, especially in high-pressure pumps in fuel injection systems. The roller tappet of a piston pump used as a high pressure pump is therefore exposed to heavy loads. The reduction or avoidance of thermally induced stresses in the roller tappet consequently not only increases the service life of the piston pump, but with it also the service life of the entire fuel injection system.

Zeichnungen

  • Fig.1 zeigt eine Kolbenpumpe mit einem Rollenstößel.
  • Fig.2 zeigt den erfindungsgemäßen Rollenstößel aus der Fig.1 in einer Seitenansicht.
  • Fig.3 zeigt einen beispielhaften Rollenstößel.
drawings
  • Fig. 1 shows a piston pump with a roller tappet.
  • Fig. 2 shows the roller tappet according to the invention from FIG Fig. 1 in a side view.
  • Fig. 3 shows an exemplary roller tappet.

Beschreibungdescription

Fig.1 zeigt eine Kolbenpumpe 1 mit einem Pumpengehäuse 20. In dem Pumpengehäuse 20 sind eine Nockenwelle 21, ein Rollenstößel 2 und ein Pumpkolben 10 angeordnet. Der Rollenstößel 2 umfasst einen Stößelkörper 15, einen Rollenschuh 3, eine Laufrolle 4 und einen Bolzen 5. Fig. 1 shows a piston pump 1 with a pump housing 20. A camshaft 21, a roller tappet 2 and a pump piston 10 are arranged in the pump housing 20. The roller tappet 2 comprises a tappet body 15, a roller shoe 3, a roller 4 and a bolt 5.

Der Rollenschuh 3 ist im Stößelkörper 15 angeordnet; in alternativen Ausführungsformen können der Stößelkörper 15 und der Rollenschuh 3 auch einstückig ausgeführt sein. Der Bolzen 5 ist im Rollenschuh 3 gelagert. Dazu sind im Rollenschuh 3 ein erstes Lagerauge 6 mit einer ersten Breite b6 und ein zweites Lagerauge 7 mit einer zweiten Breite b7 ausgebildet, in denen der Bolzen 5 gelagert bzw. eingepresst ist. Die Laufrolle 4 ist drehbar auf dem Bolzen 5 gelagert.The roller shoe 3 is arranged in the tappet body 15; In alternative embodiments, the tappet body 15 and the roller shoe 3 can also be made in one piece. The bolt 5 is mounted in the roller shoe 3. For this purpose, a first bearing eye 6 with a first width b6 and a second bearing eye 7 with a second width b7 are formed in the roller shoe 3, in which the bolt 5 is mounted or pressed. The roller 4 is rotatably mounted on the bolt 5.

Ein an der Nockenwelle 21 ausgebildeter Nocken 22 wirkt mit der Laufrolle 4 zusammen, so dass die Laufrolle 4 bei einer Rotation der Nockenwelle 21 auf dem Nocken 22 abrollt. Auf der dem Nocken 22 gegenüberliegenden Seite ist der Rollenschuh 3 mit dem Pumpkolben 10 wirkverbunden. Eine Feder 25 spannt den Pumpkolben 10 unter Zwischenlage einer Unterlegscheibe 26 gegen den Rollenschuh 3 vor.A cam 22 formed on the camshaft 21 interacts with the roller 4, so that the roller 4 rolls on the cam 22 when the camshaft 21 rotates. On the side opposite the cam 22, the roller shoe 3 is operatively connected to the pump piston 10. A spring 25 biases the pump piston 10 against the roller shoe 3 with the interposition of a washer 26.

Fig.2 zeigt den Rollenstößel 2 aus der Fig.1 in einer Seitenansicht. Die Seitenansicht zeigt den Rollenschuh 3, die Laufrolle 4, den Bolzen 5 und das erste Lagerauge 6. Im ersten Lagerauge 6 ist eine Ausnehmung 8 ausgebildet. Die Ausnehmung 8 verläuft über die gesamte Wandstärke des ersten Lagerauges 6 in Form eines durchgängigen Schlitzes, so dass das erste Lagerauge 6 in einen ersten Lagerschenkel 6a und einen zweiten Lagerschenkel 6b unterteilt ist, wobei der erste Lagerschenkel 6a einseitig von dem zweiten Lagerschenkel 6b getrennt ist. Eine Innenfläche 6c des ersten Lagerauges 6, in die der Bolzen 5 eingeklemmt bzw. eingepresst ist, ist somit aufgrund der Ausnehmung 8 vergleichsweise stark elastisch ausgebildet. Fig. 2 shows the roller tappet 2 from Fig. 1 in a side view. The side view shows the roller shoe 3, the roller 4, the bolt 5 and the first bearing eye 6. A recess 8 is formed in the first bearing eye 6. The recess 8 runs over the entire wall thickness of the first bearing eye 6 in the form of a continuous slot, so that the first bearing eye 6 is divided into a first bearing leg 6a and a second bearing leg 6b, the first bearing leg 6a being separated on one side from the second bearing leg 6b . An inner surface 6c of the first bearing eye 6, into which the bolt 5 is clamped or pressed, is thus made comparatively highly elastic due to the recess 8.

Wie zuvor erwähnt, kann in einer vorteilhaften Weiterbildung in dem zweiten Lagerauge eine weitere Ausnehmung ausgebildet sein. Fig.3 zeigt einen beispielhaften Rollenstößel 2 in einer vorteilhaften Weiterbildung. Die Ausnehmung ist hierbei in dem Lagerauge 6 nicht durchgängig über die gesamte Wandstärke des Lagerauges 6 ausgebildet, sondern führt lediglich zu einer lokalen Verringerung der Wandstärke des ersten Lagerauges 6 in diesem Bereich. Dadurch ist auch in dieser vorteilhaften Weiterbildung die Innenfläche 6c elastisch aufweitbar gestaltet, das heißt, dass im Bereich der Ausnehmung 8 das Lagerauge 6 vergleichsweise weich gestaltet ist.As mentioned above, in an advantageous development, a further recess can be formed in the second bearing eye. Fig. 3 shows an exemplary roller tappet 2 in an advantageous development. In this case, the recess in the bearing eye 6 is not formed continuously over the entire wall thickness of the bearing eye 6, but only leads to a local reduction in the wall thickness of the first bearing eye 6 in this area. As a result, in this advantageous development too, the inner surface 6c is designed to be elastically expandable, that is to say that the bearing eye 6 is designed to be comparatively soft in the region of the recess 8.

Die Funktionsweise der Kolbenpumpe 1 ist wie folgt:
Die Nockenwelle 21 wird von einer nicht dargestellten Antriebseinheit, beispielsweise von einem mit einer Brennkraftmaschine verbundenen Zahnriemen, angetrieben. Dadurch führt der Nocken 22 eine Rotationsbewegung aus und beschreibt eine Nockenbahn. Der mit dem Nocken 22 über die Laufrolle 4 wirkverbundene Rollenstößel 2 führt aufgrund der Nockenbahn eine translatorische Auf- und Abwärtsbewegung im Pumpengehäuse 20 aus, wobei die Richtung der Bewegung senkrecht zur Achse der Nockenwelle 21 verläuft. Mit dem Rollenstößel 2 führt auch der Pumpkolben 10 die Auf- und Abwärtsbewegung durch und verdichtet dadurch ein Fluid auf der dem Rollenstößel 2 gegenüberliegenden Seite in einem nicht dargestellten Verdichtungsraum. Beispielsweise kann so der Kraftstoff eines Kraftstoffeinspritzsystems in der Kolbenpumpe 1 unter Hochdruck gebracht werden.The functioning of the piston pump 1 is as follows:
The camshaft 21 is driven by a drive unit (not shown), for example by a toothed belt connected to an internal combustion engine. As a result, the cam 22 executes a rotational movement and describes a cam path. The roller tappet 2, which is operatively connected to the cam 22 via the roller 4, executes a translatory upward and downward movement in the pump housing 20 due to the cam track, the direction of movement being perpendicular to the axis of the camshaft 21. With the roller tappet 2, the pump piston 10 also performs the upward and downward movement and thereby compresses a fluid on the side opposite the roller tappet 2 in a compression chamber (not shown). For example, the fuel of a fuel injection system in the piston pump 1 can be brought under high pressure in this way.

Die Kolbenpumpe 1 ist im Betrieb Temperaturänderungen ausgesetzt, die Längenänderungen der Bauteile zur Folge haben. Erfindungsgemäß ist nun die Verbindung zwischen dem Bolzen 5 und dem ersten Lagerauge 6 elastischer bzw. weicher gestaltet als die Verbindung zwischen dem Bolzen 5 und dem zweiten Lagerauge 7. Dadurch kann der Bolzen 5 bei thermischen Belastungen eine Relativbewegung in seiner Achsrichtung zum ersten Lagerauge 6 ausführen. Thermische Spannungen im Bolzen 5 und im Rollenschuh 3 werden dadurch verringert oder sogar vermieden.The piston pump 1 is exposed to temperature changes during operation, which result in changes in the length of the components. According to the invention, the connection between the bolt 5 and the first bearing eye 6 is more elastic or softer than the connection between the bolt 5 and the second bearing eye 7 . Thermal stresses in the bolt 5 and in the roller shoe 3 are thereby reduced or even avoided.

Die unterschiedliche Gestaltung der Steifigkeiten der Verbindungen in den beiden Lageraugen 6, 7 kann dabei beispielsweise folgendermaßen ausgeführt werden:

  • Das Übermaß der beiden Pressverbände zwischen dem Bolzen 5 und den beiden Lageraugen 6, 7 ist im ersten Lagerauge 6 geringer ausgeführt als im zweiten Lagerauge 7.
  • Die Reibkraft des Pressverbands zwischen dem Bolzen 5 und dem ersten Lagerauge 6 ist geringer als die Reibkraft des Pressverbands zwischen dem Bolzen 5 und dem zweiten Lagerauge 7, beispielsweise indem die erste Breite b6 geringer ist als die zweite Breite b7.
  • Das erste Lagerauge 6 ist weicher gestaltet als das zweite Lagerauge 7, beispielsweise durch die Ausnehmung 8.
The different design of the stiffness of the connections in the two bearing eyes 6, 7 can be implemented as follows, for example:
  • The oversize of the two interference fits between the bolt 5 and the two bearing eyes 6, 7 is made smaller in the first bearing eye 6 than in the second bearing eye 7.
  • The frictional force of the interference fit between the bolt 5 and the first bearing eye 6 is less than the frictional force of the interference fit between the bolt 5 and the second bearing eye 7, for example in that the first width b6 is less than the second width b7.
  • The first bearing eye 6 is designed to be softer than the second bearing eye 7, for example due to the recess 8.

Claims (10)

  1. Reciprocating pump (1) having a roller tappet (2) and having a pump plunger (10) which is operatively connected to the roller tappet (2), wherein the roller tappet (2) has a roller support (3), a roller (4) and a pin (5), wherein a first bearing eye (6) and a second bearing eye (7) are formed in the roller support (3), wherein the pin (5) is mounted in the first bearing eye (6) and in the second bearing eye (7), and wherein the roller (4) is arranged on the pin (5) in a rotatable manner,
    wherein the pin (5) is mounted more flexibly in the first bearing eye (6) than in the second bearing eye (7), characterized in that a cutout (8) is formed in the first bearing eye (6), wherein the cutout (8) is a continuous slot, so that the first bearing eye (6) comprises two bearing legs which are separated from one another on one side.
  2. Reciprocating pump (1) according to Claim 1, characterized in that the roller support (3) is arranged in a tappet housing (15).
  3. Reciprocating pump (1) according to Claim 1 or 2, characterized in that the first bearing eye (6) has a first width (b6) and the second bearing eye (7) has a second width (b7), wherein the first width (b6) is smaller than the second width (b7).
  4. Reciprocating pump (1) according to one of Claims 1 to 3,
    characterized in that the cutout (8) is a reduction of the wall thickness of the first bearing eye (6).
  5. Reciprocating pump (1) according to one of Claims 1 to 4,
    characterized in that the first bearing eye (6) is expandable in a flexible manner.
  6. Reciprocating pump (1) according to one of Claims 1 to 5,
    characterized in that the pin (5) is clamped into the first bearing eye (6) and pressed into the second bearing eye (7).
  7. Reciprocating pump (1) according to one of Claims 1 to 6,
    characterized in that a further cutout is formed in the second bearing eye (7).
  8. Reciprocating pump (1) according to Claim 7, characterized in that the further cutout is a reduction of the wall thickness of the second bearing eye (7).
  9. Reciprocating pump (1) according to either of Claims 7 and 8,
    characterized in that the pin (5) is clamped into the first bearing eye (6) and into the second bearing eye (7) .
  10. Fuel injection system having a reciprocating pump (1) according to one of the preceding claims.
EP15736837.4A 2014-09-15 2015-07-14 Piston pump Active EP3194770B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014218489.4A DE102014218489A1 (en) 2014-09-15 2014-09-15 piston pump
PCT/EP2015/066068 WO2016041655A1 (en) 2014-09-15 2015-07-14 Reciprocating pump

Publications (2)

Publication Number Publication Date
EP3194770A1 EP3194770A1 (en) 2017-07-26
EP3194770B1 true EP3194770B1 (en) 2021-09-08

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ID=53546223

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Application Number Title Priority Date Filing Date
EP15736837.4A Active EP3194770B1 (en) 2014-09-15 2015-07-14 Piston pump

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US (1) US10100796B2 (en)
EP (1) EP3194770B1 (en)
JP (1) JP6467501B2 (en)
CN (1) CN106715886A (en)
DE (1) DE102014218489A1 (en)
WO (1) WO2016041655A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014220839B4 (en) * 2014-10-15 2016-07-21 Continental Automotive Gmbh High-pressure pump for a fuel injection system of an internal combustion engine
DE102014220937B4 (en) 2014-10-15 2016-06-30 Continental Automotive Gmbh Drive device for driving a high-pressure fuel pump and high-pressure fuel pump
KR102417607B1 (en) * 2020-11-19 2022-07-06 주식회사 현대케피코 Torsion protecting structure of roller for high pressure fuel pump

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK147186C (en) * 1981-05-06 1984-10-29 B & W Diesel As DRIVING MECHANISM FOR A FUEL PUMP FOR A REMOTELABLE TOTAL SHOCK ENGINE
DE4225363A1 (en) * 1992-07-31 1994-02-03 Bosch Gmbh Robert Fuel injection pump for internal combustion engines
DE4227854B4 (en) * 1992-08-22 2005-12-15 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
JPH1054321A (en) * 1996-08-08 1998-02-24 Toyota Motor Corp Roller bush for fuel injection pump
DE102007006320A1 (en) * 2007-02-08 2008-08-14 Schaeffler Kg Mechanical roller tappet for an internal combustion engine
JP4788705B2 (en) * 2007-11-14 2011-10-05 トヨタ自動車株式会社 Lifter caulking structure
DE102010022318B4 (en) * 2010-06-01 2017-09-07 Schaeffler Technologies AG & Co. KG roller plunger
DE102010030498A1 (en) 2010-06-24 2011-12-29 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump
DE102010063363A1 (en) * 2010-12-17 2012-06-21 Robert Bosch Gmbh high pressure pump
DE102011003678A1 (en) * 2011-02-07 2012-08-09 Robert Bosch Gmbh high pressure pump
DE102011076022A1 (en) * 2011-05-18 2012-11-22 Robert Bosch Gmbh Roller tappet, in particular a piston pump

Also Published As

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US20170260947A1 (en) 2017-09-14
WO2016041655A1 (en) 2016-03-24
US10100796B2 (en) 2018-10-16
DE102014218489A1 (en) 2016-03-17
JP2017527734A (en) 2017-09-21
EP3194770A1 (en) 2017-07-26
JP6467501B2 (en) 2019-02-13
CN106715886A (en) 2017-05-24

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