DE102009003054A1 - high pressure pump - Google Patents

high pressure pump

Info

Publication number
DE102009003054A1
DE102009003054A1 DE102009003054A DE102009003054A DE102009003054A1 DE 102009003054 A1 DE102009003054 A1 DE 102009003054A1 DE 102009003054 A DE102009003054 A DE 102009003054A DE 102009003054 A DE102009003054 A DE 102009003054A DE 102009003054 A1 DE102009003054 A1 DE 102009003054A1
Authority
DE
Germany
Prior art keywords
roller
cam
radius
tread
pressure 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.)
Withdrawn
Application number
DE102009003054A
Other languages
German (de)
Inventor
Andreas Dutt
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to DE102009003054A priority Critical patent/DE102009003054A1/en
Publication of DE102009003054A1 publication Critical patent/DE102009003054A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02Pumps 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
    • F02M59/10Pumps 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
    • F02M59/102Mechanical drive, e.g. tappets or cams
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/128Varying injection timing by angular adjustment of the face-cam or the rollers support
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06Pumps peculiar thereto
    • F02M45/063Delivery stroke of piston being divided into two or more parts, e.g. by using specially shaped cams
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44Details, 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
    • F02M59/445Selection of particular materials
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/02Fuel-injection apparatus having means for reducing wear

Abstract

A high-pressure pump (1), which serves in particular as a radial or inline piston pump for fuel injection systems of air-compressing, self-igniting internal combustion engines, has a pump assembly (13) and a drive shaft (6) which comprises a cam (9) associated with the pump assembly (13). In this case, the pump assembly (13) comprises a roller (25) which rolls with its roller surface (35) on a running surface (10) of the cam (9). A Wälzbeanspruchbarkeit the roller (25) on the roller surface (35) of the roller (25) and a Wälzbeanspruchbarkeit (9) on the running surface (10) of the cam (9) are given the same size. In the highly dynamic stress of the cam (9) and the roller (25) during operation, this results in a critical threshold voltage for both components (9, 25), which is equally critical for both components (9, 25).

Description

  • State of the art
  • The The invention relates to a high-pressure pump, in particular a radial or inline piston pump. Specifically, the invention relates to the field fuel pumps for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • From the DE 10 2005 046 670 A1 a high pressure pump for a fuel injector of an internal combustion engine is known. The known high-pressure pump has a multipart pump housing, in which at least one pump element is arranged. The pump element comprises a driven by a drive shaft in a stroke pump piston which is slidably guided in a cylinder bore of a portion of the pump housing and defines a pump working space therein. Here, the drive shaft has a cam, wherein the pump piston is driven by the cam of the drive shaft in the radial direction to a rotational axis of the drive shaft. Between the pump piston and the cam of the drive shaft, a plunger is arranged, via which the pump piston is supported via a roller on the cam of the drive shaft. In the plunger, a support element is used, in which the roller is rotatably mounted, wherein the roller rolls on the cam of the drive shaft. The axis of rotation of the roller is in this case approximately parallel to the axis of rotation of the drive shaft.
  • The from the DE 10 2005 046 670 A1 known high pressure pump has the disadvantage that in operation a swelling stress of the cam and the roller occurs, which leads to a material fatigue.
  • Disclosure of the invention
  • The High-pressure pump according to the invention with the features of claim 1 has the advantage that a reliable Operation, in particular improved durability of the cam and / or the roller is achieved. Specifically, the cam and the roller in view of the swelling stress occurring during operation improved designed.
  • By the measures listed in the dependent claims are advantageous developments of specified in claim 1 High pressure pump possible.
  • Advantageous it is that a radius of the roller is smaller than a radius of curvature of the cam at a point of the tread on which the Roller is in a top dead center of the pump assembly, and that a modulus of elasticity of a pulley material, from which the roller at least on its roller surface is smaller than a Young's modulus of one Cam material from which the cam at least on its tread is formed. This allows for different geometries of Caster and the cam the expression of a critical Threshold voltage for the roller and the cam during operation be interpreted equally critical. This is an optimization in terms of a yield strength of the roller and a yield strength of the Cam possible. At top dead center is the Hertzian pressure on the roller surface of the roller the same size as the Hertzian pressure on the tread of the cam. The Hertzian pressure must be smaller than the yield strength the roller or the cam. In an advantageous way can by the adapted design of the roller to the cam the fatigue of the two components roller and cam optimized become.
  • Advantageous it is that the radius of the roller is smaller than the radius of curvature of the cam at the location of the tread at which the caster abuts in a top dead center of the pump assembly and that the Roller has at least one bore, at least partially extends in the direction of a rotation axis of the roller. Here is it is further advantageous that the bore with respect to the axis of rotation the roller at least substantially as axial or at least is designed substantially as a coaxial bore and / or that the bore is designed as a through hole extending from one side of the roller extends to another side of the roller. This allows for different geometries at top dead center a reduction in the stiffness of the roller in the area of its Roll surface can be achieved.
  • Advantageous it is also that the radius of the roller is smaller than the radius of curvature of the cam at the location of the tread at which the caster abuts in a top dead center of the pump assembly, and that at least a compressive residual stress of the roller on its roller surface is increased. Specifically, it is advantageous that the roll surface case hardened and / or shot peened and / or rolled and / or nitrided and / or nitrocarburised. hereby can with different geometries of the roller and the cam at top dead center, the rolling resistance of the roller through Incorporation of compressive residual stress on the surface increased become. This is an advantageous adaptation of the roller possible at the cams.
  • It is advantageous that the radius of the roller is greater than the radius of curvature of the cam at the location of the tread on which the Laufrol le is in a top dead center of the pump assembly, and that the modulus of elasticity of the roller material, from which the roller is formed at least on its roller surface, is greater than the modulus of elasticity of the cam material from which the cam is formed at least on its tread. This allows an advantageous adaptation of the roller and the cam to each other. In this case, it is also possible that at least one compressive residual stress of the cam is increased at its tread.
  • Advantageous it is that a modulus of elasticity and / or a rolling resistance and / or a transverse strain number of the roller material, from the the roller formed at least on its roller surface is, and a modulus of elasticity and / or a rolling resistance and / or a transverse strain number of the cam material from which the Cam is formed at least on its tread, respectively at least approximately the same size are and that a radius of the roller and a radius of curvature of the Cam in the area of a point of the tread at the the tread at a top dead center of the pump assembly is present, at least approximately the same size specified are. For example, the roller and the cam be made of the same or comparable steels, in terms of moduli of elasticity, rolling resistance and the transverse strain number are the same or comparable designed. In this case, the radius of curvature of the cam is in the range of top dead center at least approximately equal to Radius of the roller designed so that a favorable adjustment results. It is also advantageous that the radius of the roller and the radius of curvature of the cam at the location of the tread, at the the roller in the top dead center of the pump assembly is less than 5% different from each other.
  • preferred Embodiments of the invention are in the following Description with reference to the accompanying drawings, in which corresponding elements with matching reference numerals are provided, explained in more detail. It shows:
  • 1 a high pressure pump in a schematic, axial sectional view according to an embodiment of the invention and
  • 2 an excerpted section through the in 1 illustrated high-pressure pump along the designated II section line.
  • 1 shows a high pressure pump 1 in a schematic, axial sectional view according to a first embodiment of the invention. The high pressure pump 1 can be used in particular as a radial or inline piston pump for fuel injection systems of air-compressing, self-igniting internal combustion engines. Specifically, the high pressure pump is suitable 1 for a fuel injection system with a common rail that stores diesel fuel under high pressure. The high-pressure pump according to the invention 1 However, it is also suitable for other applications.
  • The high pressure pump 1 has a multi-part housing 2 on. In this embodiment, the housing consists 2 from the housing parts 3 . 4 . 5 , wherein the housing part 3 a main body, the housing part 4 a cylinder head and the housing part 5 one on the main body 3 attached flange represents.
  • The high pressure pump 1 has a drive shaft 6 on that at campsites 7 . 8th in the housing parts 3 . 5 is stored. Between the bearings 7 . 8th has the drive shaft 6 a cam 9 on. The cam 9 is configured in this embodiment as a double cam. The cam 9 can also be configured as a single or as another multiple cam.
  • The housing part 3 the high pressure pump 1 has a guide hole 12 on, in which a pump assembly 13 is arranged. The cam 9 is the pump assembly 13 assigned. Depending on the design of the high-pressure pump 1 can also use several of the pump assembly 13 be provided corresponding pump assemblies. Such pump assemblies can the cam 9 or another cam, which is the cam 9 corresponds, to be assigned. As a result, depending on the embodiment, a radial or piston pump can be realized.
  • The designed as a cylinder head housing part 4 has an approach 14 on, in the guide hole 12 extends. The approach 14 has a cylinder bore 15 on, in which a piston 16 in the direction of an axis 17 the guide hole 12 slidably guided, as indicated by a double arrow 18 is illustrated. The piston 16 limits a pump work space 19 in the cylinder bore 15 , About one on the housing part 4 provided inlet valve 20 is fuel from a fuel channel 21 into the pump workroom 19 introduced. Furthermore, on the housing part 4 an outlet valve 22 provided via the high pressure fuel from the pump working space 19 to a fuel channel 13 is feasible. The fuel channel 13 For example, it may be connected to a common rail to supply high pressure fuel to the common rail.
  • The pump assembly 13 has a roller 25 on top of a roller shoe 26 up is taken. The roller shoe 26 is in a substantially hollow cylindrical tappet body 27 used. Furthermore, the plunger body 27 with a disk-shaped driving element 28 connected to the piston 16 above a covenant 29 of the piston 16 embraces. This is the piston 16 about his covenant 29 in contact with the roller shoe 26 held. Further, a piston spring 30 provided on the ram body 27 and / or the entrainment element 28 acts and thus the ram body 27 together with the piston 16 towards the roller 25 acted upon by a certain spring force. This causes the piston 16 with his covenant 29 , the roller shoe 26 , the role 25 and a tread 10 of the cam 9 each against each other, and this mutual contact even at high speeds of the high-pressure pump 1 is guaranteed.
  • In operation of the high pressure pump 1 is characterized by the double arrow 18 illustrated float's reciprocation 16 achieved, so that the promotion of high-pressure fuel to the common rail takes place. During a pump stroke of the piston 16 for conveying fuel to the common rail via the fuel channel 23 acts a relatively large pumping force F ( 2 ) over the roller shoe 26 on the roller 25 , The roller 25 relies on the tread 10 from.
  • In operation of the high pressure pump 1 rotates the drive shaft 6 around an axis 31 , Furthermore, the roller is running 25 on the tread 10 of the cam 9 from. A rotation axis 32 the roller 25 is at least approximately parallel to the axis 31 the drive shaft 6 oriented. The roller 25 has a roll surface 35 on. The roller 25 rolls with its roll surface 35 in operation on the tread 10 of the cam 9 from.
  • The high pressure pump 1 of the embodiment is hereinafter also with reference to the 2 described in further detail.
  • 2 shows an excerpted section through the in 1 illustrated high-pressure pump 1 along the section line marked II. This shows the 2 a situation in which a top dead center of the pump assembly 13 is reached. The roller 25 lies here with their role surface 35 at one point 36 the tread 10 of the cam 9 at. In this position or in the region of this position, the highest stress of the roller occurs 25 as well as the cam 9 on. This is the maximum delivery stroke of the piston 16 the pump assembly 13 achieved, so the maximum, from the high pressure pump 1 producible pressure in the pump working space 19 consists. This affects a correspondingly large force F.
  • The roller 25 and the cam 9 can be made of hardened high strength tool steels. Here are a geometric design and a roller material of the roller 25 and a geometric configuration of the cam and a cam material of the cam 9 chosen so that a Wälzbeanspruchbarkeit the roller 25 and a rolling load capacity of the cam 9 on the tread 10 of the cam 9 at least approximately the same size are given. In this embodiment, specifically, the rolling load capacity of the cam 9 at the point 36 his tread 10 relevant, since here a maximum rolling load of the cam 9 occurs. Due to the design of the cam 9 as a double cam 9 occurs a correspondingly large Wälzbeanspruchung also at another location 37 the tread 10 of the cam 9 on. The spot 37 is with respect to the axis 31 the drive shaft 6 opposite to the site 36 on the tread 10 arranged.
  • The roller 35 is at least approximately cylindrical in shape. The roller 25 points with respect to its roll surface 35 a radius 38 on. In addition, the cam has 9 regarding his tread 10 a circumferentially varying radius of curvature. Because the highest rolling load of the cam 9 in the field of jobs 36 . 37 occurs is a radius of curvature 39 at the point 36 relevant to the roller 25 in the top dead center of the pump assembly 13 on the tread 10 is applied. For the job 37 this results in a corresponding radius of curvature 40 , which equals the radius of curvature 39 is.
  • Depending on the design of the high-pressure pump 1 can the radius 38 the roller 25 equal, smaller or larger than the radius of curvature 39 of the cam 9 be.
  • In the in the 1 illustrated position of the cam 9 at top dead center of the pump assembly 13 is the Hertzian pressure on the tread 10 of the cam 9 as well as the roll surface 35 the roller 25 for both components 9 . 25 same size. This Hertzian pressure must be less than the yield strength of the components roller for reliable operation 25 and cams 9 , Since the stress during operation is highly dynamic, fatigue of the roller is in view of a reliable operation 25 and / or fatigue of the cam 9 significant. The swelling stress of the roller 25 and the cam 9 has its maximum below the roller surface 35 or the tread 10 , Furthermore, the swelling load is dependent on the stress, the geometry, in particular the radius 38 the roller 25 and the radii of curvature 39 . 40 in the places 36 . 37 , and the elastic modulus of the roller 25 or the cam 9 , For a reliable Operation over the life of the high-pressure pump 1 the swelling stress may be the permissible rolling strength of the components 25 . 9 used material or materials. The swelling stress affects the stronger, the smaller the radius 38 the roller 25 or the radius of curvature 39 of the cam 9 is. Thus, the component becomes 25 . 29 more heavily loaded, the smaller radius 38 or radius of curvature 39 having.
  • Advantageously, the critical threshold voltage for both components 9 . 25 Equally critical with regard to the permissible Wälzbeanspruchung designed. Examples of possible interpretations are described further below.
  • If the radius 38 the roller 25 is smaller than the radius of curvature 39 of the cam 9 , Then advantageously, a modulus of elasticity of the roller material, from which the roller 25 at least in the area of its roll surface 35 is smaller than a Young's modulus of the cam material from which the cam 9 at least in the area of his tread 10 is formed. It is also possible in this case that the roller at least one hole 41 having. Such a hole 41 allows a reduction in the stiffness of the roller 25 , in particular in the area of its roll surface 35 , The hole 41 is preferably as axial or coaxial bore 41 designed. In this embodiment, the bore 41 designed as an axial bore extending along the axis of rotation 32 the roller 25 extends. The hole 41 is in this embodiment as a through hole 41 designed. The hole 41 extends from one side 42 the roller 25 to another page 43 the roller 25 that from the side 42 turned away.
  • In the case where the radius 38 the roller 25 smaller than the radius of curvature 39 of the cam 9 at the point 36 the tread 10 , It is also advantageous that residual compressive stresses of the roller 25 on her roll surface 35 are increased. Here, the roller 25 in the area of their roll surface 35 be edited. Special is a case hardening of the roll surface 35 , a shot blasting of the roller surface 35 , a rolling of the roller surface 35 , nitriding the roll surface 35 or also nitrocarburizing the roll surface 35 possible. As a result, the rolling resistance of the roller 25 , in particular the roll surface 35 the roller 25 , by introducing compressive residual stresses on the roller surface 35 increase.
  • In a case where the radius 38 the roller 25 is greater than the radius of curvature 39 of the cam 9 It is advantageous that the modulus of elasticity of the pulley material from which the pulley 25 is greater than the Young's modulus of the cam material from which the cam 9 at least on his tread 10 is formed. As a result, a load compensation is possible to the same or at least a comparable load for both the roller 25 as well as for the cam 9 to achieve. Also possible is a machining, in particular a surface treatment of the cam 9 , This can be done according to a surface treatment of the roll surface 35 the roller 25 be executed.
  • In a case where the radius 38 the roller 25 and the radius of curvature 39 of the cam 9 at the point 36 the tread 10 at least approximately the same size, it is advantageous that the roller material of the roller 25 and the cam material of the cam 9 each have at least approximately an equal modulus of elasticity, at least approximately equal rolling resistance and / or at least approximately equal in transverse strain number. As a result, both a comparable geometry and a pairing of comparable or the same materials for the roller 25 and the cam 9 in the field of jobs 36 . 37 allows. As a result, the same or at least a comparable stress can be achieved.
  • The radius 38 the roller 25 and the radius of curvature 39 of the cam 9 preferably differ by less than 5% from each other.
  • The Invention is not limited to the described embodiments limited.
  • QUOTES INCLUDE IN THE DESCRIPTION
  • This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.
  • Cited patent literature
    • - DE 102005046670 A1 [0002, 0003]

Claims (10)

  1. High pressure pump ( 1 ), in particular radial or inline piston pump for fuel injection systems of air-compressing, self-igniting internal combustion engines, with at least one pump assembly ( 13 ) and a drive shaft ( 6 ), which at least one of the pump assembly ( 13 ) associated cam ( 9 ), wherein the pump assembly ( 13 ) a roller ( 25 ) having a roller surface ( 35 ), and wherein the roller ( 25 ) on a tread ( 10 ) of the cam ( 9 ), characterized in that a rolling load capacity of the roller ( 25 ) on the roller surface ( 35 ) of the roller ( 25 ) and a rolling load capacity of the cam ( 9 ) on the tread ( 10 ) of the cam ( 9 ) are predetermined at least approximately the same size.
  2. High pressure pump according to claim 1, characterized in that a radius ( 38 ) of the roller ( 25 ) is smaller than a radius of curvature ( 39 ) of the cam ( 9 ) in one place ( 36 ) of the tread ( 10 ), on which the roller ( 25 ) in a top dead center of the pump assembly ( 13 ) and that a modulus of elasticity of a caster material from which the caster ( 25 ) at least on its roll surface ( 35 ) is smaller than a Young's modulus of a cam material from which the cam ( 9 ) at least on its tread ( 10 ) is formed.
  3. High-pressure pump according to claim 1 or 2, characterized in that a radius ( 38 ) of the roller ( 25 ) is smaller than a radius of curvature ( 39 ) of the cam ( 9 ) in one place ( 36 ) of the tread ( 10 ), on which the roller ( 25 ) in a top dead center of the pump assembly ( 13 ) and that the roller ( 25 ) at least one bore ( 41 ), which at least partially in the direction of a rotation axis ( 32 ) of the roller ( 25 ).
  4. High pressure pump according to claim 3, characterized in that the bore ( 41 ) with respect to the axis of rotation ( 32 ) of the roller ( 25 ) at least substantially as an axial or at least substantially coaxial bore ( 41 ) and / or that the bore ( 41 ) as a through hole ( 41 ), which extends from one side ( 42 ) of the roller ( 25 ) to another page ( 43 ) of the roller ( 25 ).
  5. High-pressure pump according to one of claims 1 to 4, characterized in that a radius ( 38 ) of the roller ( 25 ) is smaller than a radius of curvature ( 39 ) of the cam ( 9 ) in one place ( 36 ) of the tread ( 10 ), on which the roller ( 25 ) in a top dead center of the pump assembly ( 13 ) is applied, and that at least one compressive residual stress of the roller ( 25 ) on its roll surface ( 35 ) is increased.
  6. High-pressure pump according to claim 5, characterized in that the roller surface ( 35 ) of the roller ( 25 ) case hardened and / or shot peened and / or rolled and / or nitrided and / or nitrocarburised.
  7. High pressure pump according to claim 1, characterized in that a radius ( 38 ) of the roller ( 25 ) is greater than a radius of curvature ( 39 ) of the cam ( 9 ) in one place ( 36 ) of the tread ( 10 ), on which the roller ( 25 ) in a top dead center of the pump assembly ( 13 ) and that a modulus of elasticity of a caster material from which the caster ( 25 ) at least on its roll surface ( 35 ) is greater than a Young's modulus of a cam material from which the cam ( 9 ) at least on its tread ( 10 ) is formed.
  8. High-pressure pump according to claim 7, characterized in that at least one compressive residual stress of the cam ( 9 ) on its tread ( 10 ) is increased.
  9. High-pressure pump according to claim 1, characterized in that a modulus of elasticity and / or a rolling resistance and / or a transverse strain number of a roller material from which the roller ( 25 ) at least on its roll surface ( 35 ) is formed, and a modulus of elasticity and / or a rolling resistance and / or a transverse strain coefficient of a cam material from which the cam ( 9 ) at least on its tread ( 10 ) is formed, in each case at least approximately the same size are given and that a radius ( 38 ) of the roller ( 25 ) and a radius of curvature ( 39 ) of the cam ( 9 ) in the area of a job ( 36 ) of the tread ( 10 ), on which the roller ( 25 ) in a top dead center of the pump assembly ( 13 ) is applied, at least approximately the same size are given.
  10. High pressure pump according to claim 9, characterized in that the radius ( 38 ) of the roller ( 25 ) and the radius of curvature ( 39 ) of the cam ( 9 ) in the place ( 36 ) of the tread ( 10 ), on which the roller ( 25 ) in the top dead center of the pump assembly ( 13 ) is less than 5% different.
DE102009003054A 2009-05-13 2009-05-13 high pressure pump Withdrawn DE102009003054A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE102009003054A DE102009003054A1 (en) 2009-05-13 2009-05-13 high pressure pump

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
DE102009003054A DE102009003054A1 (en) 2009-05-13 2009-05-13 high pressure pump
CN201080021222.1A CN102422011B (en) 2009-05-13 2010-03-22 High-pressure pump
EP10709736.2A EP2430303B1 (en) 2009-05-13 2010-03-22 High pressure pump
KR1020117026859A KR101682737B1 (en) 2009-05-13 2010-03-22 High pressure pump
PCT/EP2010/053696 WO2010130497A1 (en) 2009-05-13 2010-03-22 High pressure pump
JP2012510181A JP5491621B2 (en) 2009-05-13 2010-03-22 High pressure pump
RU2011150403/06A RU2554377C2 (en) 2009-05-13 2010-03-22 High pressure pump
US13/265,567 US20120051951A1 (en) 2009-05-13 2010-03-22 High pressure pump

Publications (1)

Publication Number Publication Date
DE102009003054A1 true DE102009003054A1 (en) 2010-11-18

Family

ID=42244773

Family Applications (1)

Application Number Title Priority Date Filing Date
DE102009003054A Withdrawn DE102009003054A1 (en) 2009-05-13 2009-05-13 high pressure pump

Country Status (8)

Country Link
US (1) US20120051951A1 (en)
EP (1) EP2430303B1 (en)
JP (1) JP5491621B2 (en)
KR (1) KR101682737B1 (en)
CN (1) CN102422011B (en)
DE (1) DE102009003054A1 (en)
RU (1) RU2554377C2 (en)
WO (1) WO2010130497A1 (en)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011082642A1 (en) 2011-09-14 2013-03-14 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump for a fuel injection device of an internal combustion engine
DE102013204327A1 (en) 2013-03-13 2014-09-18 Robert Bosch Gmbh Cylinder head blank, cylinder head and high-pressure pump for fuel injection systems
WO2014170157A1 (en) * 2013-04-17 2014-10-23 Robert Bosch Gmbh High-pressure pump
DE102013212304A1 (en) 2013-06-26 2014-12-31 Robert Bosch Gmbh high pressure pump
WO2014206607A1 (en) 2013-06-25 2014-12-31 Robert Bosch Gmbh Pump
DE102013212248A1 (en) 2013-06-26 2014-12-31 Robert Bosch Gmbh high pressure pump
DE102013212302A1 (en) 2013-06-26 2014-12-31 Robert Bosch Gmbh High pressure pump and fuel injection system with a high pressure pump
DE102013212261A1 (en) 2013-06-26 2014-12-31 Robert Bosch Gmbh high pressure pump
DE102013212146A1 (en) 2013-06-25 2015-01-08 Robert Bosch Gmbh Pump
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DE102014205260A1 (en) 2014-03-20 2015-09-24 Robert Bosch Gmbh high pressure pump
DE102014206968A1 (en) 2014-04-10 2015-10-15 Robert Bosch Gmbh High pressure pump and high pressure directional valve
DE102014219293A1 (en) 2014-09-24 2016-03-24 Robert Bosch Gmbh Pump, in particular high-pressure pump for fuel injection systems, with a sealing device
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