[go: up one dir, main page]

EP2035701B1 - Pompe à piston - Google Patents

Pompe à piston Download PDF

Info

Publication number
EP2035701B1
EP2035701B1 EP07729697A EP07729697A EP2035701B1 EP 2035701 B1 EP2035701 B1 EP 2035701B1 EP 07729697 A EP07729697 A EP 07729697A EP 07729697 A EP07729697 A EP 07729697A EP 2035701 B1 EP2035701 B1 EP 2035701B1
Authority
EP
European Patent Office
Prior art keywords
bearing
drive shaft
internal combustion
combustion engine
engine according
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.)
Not-in-force
Application number
EP07729697A
Other languages
German (de)
English (en)
Other versions
EP2035701A1 (fr
Inventor
Siegfried Tisch
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.)
IHO Holding GmbH and Co KG
Original Assignee
Schaeffler KG
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 Schaeffler KG filed Critical Schaeffler KG
Publication of EP2035701A1 publication Critical patent/EP2035701A1/fr
Application granted granted Critical
Publication of EP2035701B1 publication Critical patent/EP2035701B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • 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
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders

Definitions

  • the invention relates to a direct-injection internal combustion engine having a high-pressure fuel supply to the internal combustion engine piston pump having a pump housing and a drive shaft for actuating one or more pump plunger, which are aligned with respect to the drive shaft radially in the pump housing, wherein the drive shaft at one or more bearings, the run between a shaft inlet opening of the pump housing and the shaft input opening opposite the housing rear wall, rotatably mounted and co-axially rotatably connected to a serving for the actuation of intake and / or exhaust valves of the internal combustion engine camshaft.
  • Piston pumps for injection systems of internal combustion engines are known in various configurations in the prior art. So goes for example from the DE 102 08 574 A1 a radial piston pump forth, which has a arranged on an eccentric portion of the drive shaft cam ring as a drive element for the pump plunger.
  • the drive shaft is rotatably mounted in the pump housing via a ball bearing arranged in the shaft input opening and in the region of the housing rear wall in a sliding bearing.
  • An exemplary embodiment of the piston pump common feature is that in each case arranged in the region of the rear housing bearing requires an end-side shaft journal of the drive shaft, which connects to the actual drive element in the form of eccentrically mounted cam ring or the cam.
  • the axial space required by the shaft journal can be critical with regard to the pump length when the piston pump is arranged in the cylinder head region of the internal combustion engine. This is in addition to the permanent endeavor to make the engine compact and space-saving, currently also justified in that the required to meet more stringent pedestrian protection clearance between the hood of a vehicle on the one hand and the built-in vehicle internal combustion engine including its attachments on the other hand is unconditionally adhered.
  • the piston pump of this document is also an embodiment without its own drive shaft, which may be used in conjunction with an extended camshaft which is already sufficiently stable in the internal combustion engine.
  • a piston pump driven by the drive shaft of an electric motor wherein the drive shaft is mounted on a support shaft extending from the rear wall of the pump housing.
  • the piston pump and the electric motor form a motor-pump unit for electronically controlled braking systems of motor vehicles.
  • the present invention has the object, a piston pump of the type mentioned in terms of the shortest possible length with the best possible stability of the drive shaft bearing and simultaneous weight savings educate so that the cited disadvantages or design limitations are avoided by simple means.
  • this object is achieved in that the one bearing point between an inner circumferential surface of a hollow cylindrical portion of the drive shaft and an outer circumferential surface of an outgoing from the rear wall of the housing and extending into the hollow cylindrical portion bearing journal runs. Accordingly, the overall length of the piston pump can be significantly reduced while reducing weight, that the arranged in the rear of the housing bearing point is moved into the interior of the hollow cylindrical portion of the drive shaft and thus the usually provided and the length of the piston pump significantly influential journals including the adjacent construction for the Storage facility deleted.
  • the bearing point is at the same time ensures that the storage quality of the drive shaft in the pump housing over conventional bearings at least maintained or, as will be explained below, even significantly improved.
  • the bearing journal should be formed integrally with the pump housing. While this is another post to reduce the length of the piston pump supplies, it is of course also possible to attach the bearing pin as a separate, optionally also hollow cylindrical component to the rear wall. This attachment can be done via the known connection techniques, such as press-fitting, screwing in, or screwing, welding, gluing, soldering, riveting, etc. in case of required sealing against lubricant leakage from the pump housing.
  • the drive shaft is intended to be co-axially co-axially connected to a camshaft serving to actuate intake and / or exhaust valves of the internal combustion engine.
  • a camshaft serving to actuate intake and / or exhaust valves of the internal combustion engine.
  • the rotary joint between the drive shaft and the camshaft can be designed according to a first advantageous variant as a form-fitting coupling, in which the drive shaft has a continuous longitudinal opening, in which the hollow cylindrical portion and an adjacent thereto inner longitudinal toothing extends with an external longitudinal toothing on one of Piston pump facing end portion of the camshaft is engaged.
  • At least one radial needle bearing which consists of at least a needle ring with a cage and guided therein needles.
  • the inner circumferential surface of the hollow cylindrical portion of the drive shaft can serve as an outer raceway for the needles.
  • the outer raceway of one or two radially inwardly extending and integrally formed with the drive shaft shoulders, which serve as axial contact surfaces for the needles be limited on one side or on both sides.
  • the radial needle bearing is formed as a needle sleeve with a thin-walled, inserted into the inner circumferential surface of the hollow cylindrical portion of the drive shaft outer ring.
  • the outer ring serving as an outer raceway for the needles inner lateral surface and two radially inwardly extending and serving as an axial thrust surface for the cage shoulders on.
  • the inner raceway for the needles should be formed by a trained on the outer circumferential surface of the journal inner ring. This represents a cost-effective option for the required finishing and hardening of the outer circumferential surface of the bearing journal, when the outer circumferential surface is provided directly as an inner raceway for the needles.
  • the needle sleeve and the thin-walled inner ring should form a structural unit in that the outer ring of the needle sleeve is surrounded axially by two shoulders which extend radially outwards and are integrally formed with the inner ring.
  • the two radially outwardly extending shoulders of the thin-walled inner ring can also serve as axial contact surfaces for the cage of the needle ring.
  • a particularly cost-effective axial securing of the inner ring on the bearing journal is further provided by an end-face and radially outward caulking of the bearing journal, which covers the inner ring at least partially radially.
  • the material produced during caulking, frontal Materialaufin the journal may be formed either locally, point or segment-shaped or annular circumferentially.
  • the one bearing a radial-axial bearing with the needle ring and adjacent to the needle ring arranged and preferably designed as angular contact ball bearings comprise Axial anymorelzlager, wherein the radial-axial bearing combined to one of the drive shaft and the journal separately manufactured unit is.
  • this particularly space-saving unit can be designed both for receiving axial forces in one direction and in both directions.
  • the second bearing comprises an axial roller bearing.
  • the axial rolling bearing can be designed as a ball bearing arranged in the shaft inlet opening of the pump housing, wherein the inner raceway for the balls is formed by a circumferential groove on an outer shell section of the drive shaft extending in the shaft inlet opening.
  • the Axial maybelzlager may also be formed as at least one cage and needles guided therein axial needle bearing and disposed between the rear wall of the housing and one of the rear wall facing the annular end face of the drive shaft.
  • the thrust roller bearing disposed on the second bearing can be extremely narrow due to the comparatively small axial forces on the drive shaft building, weight-saving and cost-effective. So it is possible in the embodiment as a ball bearing, for example, that this has only three balls at low, yet sufficient load rating.
  • a particularly space-saving and cost-effective storage of the drive shaft via separate radial needle bearings and axial needle bearings can also be done via the design of the mounted on the journal inner ring.
  • the inner ring should be thin-walled and, starting from the inner raceway for the needles of the radial needle bearing, have a stepped in the direction of the rear wall of the housing enlarging diameter.
  • the inner raceway goes over into a shoulder, which faces away from the rear wall with the ring end face as an axial contact surface for the cage of the radial needle bearing and centered with its outer circumferential surface of the cage of the Axialnadellagers.
  • the shoulder should pass into a radially extending outwardly between the rear wall of the housing and the annular end face of the drive shaft collar, which serves as a housing-side raceway for the needles of the Axialnadellagers.
  • the inner ring on its side opposite the collar end side has a radially inwardly extending and the bearing journal frontally cross-collar.
  • Such a collar serves as a counter surface for a mounting tool and facilitates the sliding of the inner ring on the bearing pin.
  • the drive shaft of a hardened bearing steel grade C16, 16MnCr5, C45, Cf53, C80 or 100Cr6 exist. This not only the required wear resistance in Cam-pump plunger contact ensured, but the materials mentioned are also ideal for the optionally arranged directly on the drive shaft rolling element raceways.
  • lubricant of a bearing at least one drive shaft transversely passing through hole, which opens in the region of a bearing and serves as a lubricant channel. While one or more such holes are basically also suitable for supplying lubricant to plain bearings, they represent a particularly effective and cost-effective way of supplying the aforesaid roller bearings with pressureless spray oil or oil mist.
  • the lubricant which is required for lubricating the pump tappets, then passes over the comparatively short length the lubricant hole in the tribologically highly stressed area of the rolling bearing.
  • the piston pump is used in all variants for high-pressure fuel supply to an internal combustion engine, not shown, with direct injection and is flanged in extension of a camshaft for actuating inlet and / or exhaust valves of the internal combustion engine to the cylinder head.
  • the lifting operation of one or more longitudinally movably mounted in the pump housing pump plunger is always via one or more cam lobes on the outer circumferential surface of the drive shaft.
  • extensive structural design freedom, according to which the pump tappet depending on Use case of the piston pump axially in series, can be arranged radially offset in a plane or both axially and radially.
  • FIG. 1 is a piston pump 1a with a pump housing 2, a rotatably mounted in the pump housing 2 drive shaft 3a and a longitudinally movably mounted in a tappet guide 4 of the pump housing 2 pump tappet 5, which is aligned with respect to the drive shaft 3a radially in the pump housing 2, shown.
  • the pump tappet 5 has a roller bearing roller cam 6 as a low-friction tapping element for a pump cam 7, the collection of which starts from the dashed cam base circle 8.
  • the drive shaft 3a has a continuous longitudinal opening 9 with a hollow cylindrical portion 10 for receiving a radial bearing 11 and an inner longitudinal toothing 12 adjacent thereto.
  • a corresponding outer longitudinal toothing 13 is located on one of the piston pump 1a facing end portion of the drive shaft 3a coaxially arranged camshaft 14a, which drives the drive shaft 3a via the interlocking interlocking teeth 12 and 13.
  • a running around a shaft inlet opening 15 of the pump housing 2 sealing ring 16 serves to seal the piston pump 1 a relative to the end face of the cylinder head.
  • the radial bearing point 11 is arranged between an inner circumferential surface 17 of the hollow cylindrical portion 10 of the drive shaft 3 a and an outer circumferential surface 18 of a bearing journal 19, which starts from a housing rear wall 20 and is integrally formed here with the pump housing 2.
  • the bearing 11 comprises a mounted on the outer circumferential surface 18 of the journal 19 and fixed by a housing-side retaining ring 21a inner ring 22a and designed as a needle sleeve 23 radial needle bearing 24, consisting of a needle ring 25 with cage 26 and guided therein needles 27 and a thin-walled outer ring 28 with two radially inwardly extending and serving as an axial thrust surface for the cage 26 shoulders 29.
  • To supply lubricant to the radial needle bearing 24 is a drive shaft 3a transversely passing through bore 30, which in the region of the bearing 11 opens and in the tappet guide 4 resulting lubricant into the radial needle bearing 24 passes.
  • a second, axial bearing 31 is provided in this embodiment, which here comprises an in the shaft inlet opening 15 between a shaft-side circlip 21 b and a housing-side shoulder 32a supported and designed as a deep groove ball bearings Axialmélzlager 33a.
  • a surface hardening of the drive shaft 3a can be limited to the pump cam 7 and for example done in the induction process.
  • the inventive bearing of the drive shaft 3a on the bearing pin 19 makes it possible to position the radial bearing point 11 and the pump plunger 5 in the axial direction of the drive shaft 3a to each other so that a designated 35 radial force generated as a resultant reaction force in the lifting operation of the pump plunger 5 and is supported by the bearing 11, lever arm and runs here centrally within the longitudinal extension of the bearing 11.
  • this bearing arrangement leads to a considerable increase in rigidity of the shaft bearing and beyond to a significant relief of the deep groove ball bearing, which now at most slightly negative axial forces must support and can be performed with a small required load rating according to narrow construction.
  • the bearing pin 19 is integrally formed with the pump housing 2 both in this and in the embodiments explained below. It is provided for the preparation of the bearing pin 19 that the Functional surfaces for the bearing 11 are finished with a entering through the shaft input port 15 cutting tool.
  • FIGS. 2 to 8 give a - not exhaustive - overview of further design possibilities of the piston pump according to the invention, wherein the following explanations, unless otherwise stated, are limited to the variations of the drive shaft bearing. Of course, it is up to the designer to design features of individual embodiments, in particular, depending on the number and arrangement of several pump tappets, suitably professionally to modify, combine with each other or omitted.
  • the radial needle bearing 24 is limited to the arranged between the bearing pin 19 and a drive shaft 3b needle ring 25, so that the inner circumferential surface 17 of the hollow cylindrical portion 10 directly forms the outer raceway for the needles 27.
  • an axial contact surfaces for the needles 27 serve two radially inwardly extending and integrally formed with the drive shaft 3b shoulders 36.
  • an end-side and radially outward caulking 37 of Trunnion 19 provided for axial securing the wound on the outer surface 18 of the journal 19 inner ring 22a in this case.
  • the case generated and the end face of the inner ring 22a radially overlapping material throw is formed here annularly encircling.
  • the arranged in the shaft inlet opening 15 of the pump housing 2 second bearing 31 in turn comprises a designed as a ball bearing Axialmélzlager 33b, 33a like the Axial maybelzlager according to FIG. 1 not only to support any axial forces occurring, but also for centering the pump housing relative to the drive shaft 3b and 3a, respectively.
  • the axial rolling bearing 33b is here combined with the drive shaft 3b to form a structural unit, in that the inner raceway for the balls 38 is guided by a peripheral groove running on an outer jacket section 39 of the drive shaft 3b 40a is formed.
  • the drive shaft 3b is tribologically stressed not only on the pump cam 7 but also on the outer raceway for the needles 27 (inner circumferential surface 17) and on the inner raceway for the balls 38 (circumferential groove 40a), it is particularly useful, the drive shaft 3b to perform from a use or by hardening bearing steel of the aforementioned types.
  • FIG. 3 Another embodiment of a piston pump 1 c according to the invention is made FIG. 3 seen.
  • the second axial bearing 31 is arranged in this case between the rear housing wall 20 and one of the housing rear wall 20 facing annular end face 41 of the drive shaft 3c.
  • the bearing 31 comprises an axial roller bearing 33c in the form of a short-axial needle bearing 42, also referred to as an axial needle ring, with a cage 43 centered by the inner ring 22a and needles 44 guided therein, and a thrust washer 45 abutting the rear wall 20 as a housing-side raceway for the needles 44th
  • the drive shaft 3c in this case is not driven by an internal longitudinal toothing but via a frontally extending rectangular recess 46 for receiving a two-way clutch, which compensates for a caused by component tolerances and elastic deformations radial offset between the camshaft and the drive shaft 3c.
  • FIG. 4 illustrated embodiment of a piston pump according to the invention 1d whose drive shaft 3d is formed integrally with a camshaft 14b. Since the axial position of the camshaft 14b is already fixed in a known manner via an axial bearing arranged in the cylinder head of the internal combustion engine, only the radial bearing point 11 in the form of the bearing is already provided for supporting the drive shaft 3d in the pump housing 2d FIG. 1 known needle sleeve 23 between the hollow cylindrical portion 10 and the bearing pin 19 is provided.
  • FIG. 5 upper half section again shows a separate from the camshaft drive shaft 3f with internal longitudinal teeth 12 in accordance FIG. 1 and in the shaft input port 15 arranged ball bearing according to FIG. 2 ,
  • a thin-walled trained, mounted on the bearing pin 19 and axially secured by caulking 37 inner ring 22c has in this case two radially outwardly extending and serving as axial contact surfaces for the cage 26 of the needle bearing 25 shoulders 48.
  • the serving here as an outer raceway for the needles 27 inner circumferential surface 17 of the hollow cylindrical portion 10 is continuous cylindrical without the in FIG. 2 shown shoulders 36 are performed, whereby the processing of the drive shaft 3 f is simplified.
  • FIG. 6 is a rotatably mounted on three bearings 11, 31 and 49 drive shaft 3g of a piston pump 1g shown.
  • the drive shaft 3g is analogous to the embodiment according to FIG. 3 driven by a engaging in the rectangular recess 46 two-face coupling of the camshaft, wherein for supporting bilaterally acting axial forces two Axialnadellager 42 and 50th are provided.
  • the first axial needle bearing 42 is disposed between the rear wall 20 and the facing this end face 41 of the drive shaft 3g, while the second Axialnadellager 50 between the shaft input port 15 delimiting inner wall portion 51 of the pump housing 2 and the inner wall portion 51 facing annular end surface 52 of the drive shaft 3g is arranged.
  • the shaft-side raceways for the needles 44 of both axial needle bearings 42 and 50 are formed directly by the annular end faces 41 and 52.
  • the pump housing 2 is formed in two parts and includes the shaft input port 15 limiting flange 53.
  • Such a flange is also to provide in the other embodiments in particular when the size of the shaft input port 15 does not allow passage of the pump cam 7.
  • the housing-side raceway for the arranged on the rear housing 20 needle bearing 42 is formed by a mounted on the bearing pin 19 and specially shaped, thin-walled inner ring 22d.
  • This has, starting from its inner race for the needles 27 of again designed only as a needle rim 25 radial needle bearing 24, a stepped in the direction of the rear wall 20 diameter enlarging.
  • the inner raceway passes into a shoulder 54, which faces away from the housing rear wall 20 annular end face 55 serves as an axial thrust surface for the cage 26 of the needle ring 25 and centered with its outer circumferential surface 56, the cage 43 of the Axialnadellagers 42.
  • the shoulder 54 merges into a collar 57 which extends radially outward between the housing rear wall 20 and the annular end face 41 of the drive shaft 3g and on which the needles 44 of the axial needle bearing 42 roll.
  • the inner ring 22d on its collar 57 opposite end face on a radially inwardly extending collar 58 which engages over the bearing pin 19 frontally and serves as a contact surface for an assembly tool for pushing the inner ring 22d on the bearing pin 19.
  • FIG. 7 Further embodiments of inventive piston pumps 1 h and 1i are shown with drive shafts 3h and 3i and the associated bearings 11 each in an upper and a lower half section.
  • Each drive shaft 3h and 3i has the continuous longitudinal opening 9 and two diametrically opposed rectangular recesses 46 for receiving said two-flat coupling.
  • arranged between the hollow cylindrical portion 10 and the bearing pin 19 bearings 11 include a combined radial-axial bearings 59a and 59b, each consisting of the needle ring 25 and an angular contact ball bearing designed as axial roller bearings 33d and 33e for supporting both sides acting axial forces ,
  • a necked on the bearing pin 19 and caulked inner ring 22e is provided in the radial-axial bearing 59a according to the upper half section.
  • the thrust washer 45 inserted between the inner ring 22e and the rear housing wall 20 serves as an axial thrust surface for the cage 26 of the needle wheel 25, the needles 27 rolling directly on the inner lateral surface 17 of the hollow cylindrical section 10.
  • the inner race for the balls 38 of the angular contact ball bearing is formed by a circumferential groove 40b of the inner ring 22e, while its outer race also extends on the inner circumferential surface 17 of the hollow cylindrical portion 10.
  • the radial thrust bearing 59b shown in the lower half section is combined into a unit 60 separately manufactured by the drive shaft 3i and the trunnion 19.
  • This assembly 60 also referred to as a combined needle bearing, comprises an outer ring 61 inserted into the inner circumferential surface 17 of the hollow cylindrical section 10 for forming the outer raceways for the needles 27 of the needle bearing 25 and the balls 38 of the angular contact ball bearing.
  • An inner race 22f forming the inner raceways for the needles 27 and the balls 38 is divided into two parts with a wide and a narrow portion 62 and 63 for supporting bilateral axial forces executed.
  • the assembly 60 is on the housing side defined by the front side caulking 37 and the shoulder 32b of the journal 19 and the shaft side by a shoulder 32c and the shaft side locking ring 21 b.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Rolling Contact Bearings (AREA)
  • Reciprocating Pumps (AREA)

Claims (15)

  1. Moteur à combustion interne à injection directe comprenant une pompe à piston servant à l'alimentation de carburant haute pression au moteur à combustion interne, qui présente un carter de pompe (2) et un arbre d'entraînement (3a à 3i) pour l'actionnement d'un ou de plusieurs poussoirs de pompe (5) qui sont orientés radialement dans le carter de pompe (2) par rapport à l'arbre d'entraînement (3a à 3i), l'arbre d'entraînement (3a à 3i) étant monté à rotation sur un ou plusieurs points de palier (11, 31, 49) qui s'étendent entre une ouverture d'entrée d'arbre (15) du carter de pompe (2) et une paroi arrière de carter (20) opposée à l'ouverture d'entrée d'arbre (15), et étant connecté en rotation de manière coaxiale à un arbre à cames (14a à 14c) servant à l'actionnement de soupapes d'admission et/ou d'échappement du moteur à combustion interne, caractérisé en ce que l'un des points de palier (11) s'étend entre une surface d'enveloppe intérieure (17) d'une portion cylindrique creuse (10) de l'arbre d'entraînement (3a à 3i) et une surface d'enveloppe extérieure (18) d'un tourillon de palier (19) partant de la paroi arrière du carter (20) et s'étendant dans la portion cylindrique creuse (10).
  2. Moteur à combustion interne selon la revendication 1, caractérisé en ce que le tourillon de palier (19) est réalisé d'une seule pièce avec le carter de pompe (2).
  3. Moteur à combustion interne selon la revendication 1, caractérisé en ce que l'arbre d'entraînement (3a, 3b, 3f) présente une ouverture longitudinale continue (9), dans laquelle ouverture longitudinale (9) s'étend la portion cylindrique creuse (10) et une denture longitudinale intérieure (12) adjacente à celle-ci, qui est en prise avec une denture longitudinale extérieure (13) sur une portion d'extrémité de l'arbre à cames (14a) tournée vers la pompe à piston (1a, 1b, 1f).
  4. Moteur à combustion interne selon la revendication 1, caractérisé en ce que l'arbre d'entraînement (3d, 3e) et l'arbre à cames (14b, 14c) sont réunis pour former une unité constructive connectée rigidement.
  5. Moteur à combustion interne selon la revendication 1, caractérisé en ce que l'un des points de palier (11) comprend au moins un palier à aiguilles radial (24), au moins constitué d'une couronne d'aiguilles (25) avec une cage (26) et des aiguilles (27) guidées à l'intérieur.
  6. Moteur à combustion interne selon la revendication 5, caractérisé en ce que la surface d'enveloppe intérieure (17) de la portion cylindrique creuse (10) de l'arbre d'entraînement (3b, 3c, 3f, 3g, 2h) sert de piste de roulement extérieure pour les aiguilles (27).
  7. Moteur à combustion interne selon la revendication 6, caractérisé en ce que la piste de roulement extérieure est limitée d'un côté ou des deux côtés par un ou deux épaulements (36), qui servent de surfaces d'entrée axiales pour les aiguilles (27), réalisés d'une seule pièce avec l'arbre d'entraînement (3b, 3c) et s'étendant radialement vers l'intérieur.
  8. Moteur à combustion interne selon la revendication 5, caractérisé en ce que le palier à aiguilles radial (24) est réalisé sous forme de douille à aiguilles (23) avec une bague extérieure (28) à parois minces, insérée dans la surface d'enveloppe intérieure (17) de la portion cylindrique creuse (10) de l'arbre d'entraînement (3a, 3e), laquelle bague extérieure (28) présente une surface d'enveloppe intérieure (34) servant de piste de roulement extérieure pour les aiguilles (27) ainsi que deux épaulements (29) s'étendant radialement vers l'intérieur et servant de surface d'entrée axiale pour la cage (26).
  9. Moteur à combustion interne selon la revendication 5, caractérisé en ce que la piste de roulement intérieure pour les aiguilles (27) est formée par une bague intérieure (22a à 22f) montée sur la surface d'enveloppe extérieure (18) du tourillon de palier (19).
  10. Moteur à combustion interne selon les revendications 8 et 9, caractérisé en ce que la douille à aiguilles (23) et la bague intérieure (22b) réalisée avec des parois minces forment une unité constructive, la bague extérieure (28) de la douille à aiguilles (23) étant enchâssée axialement par deux épaulements (47) s'étendant radialement vers l'extérieur et réalisés d'une seule pièce avec la bague intérieure (22b).
  11. Moteur à combustion interne selon la revendication 9, caractérisé en ce que la bague intérieure (22c) est réalisée avec des parois minces et présente deux épaulements (48) s'étendant radialement vers l'extérieur et servant de surfaces d'entrée axiales pour la cage (26).
  12. Moteur à combustion interne selon la revendication 9, caractérisé en ce que pour la fixation axiale de la bague intérieure (22a, 22c, 22e, 22f) sur le tourillon de palier (19), on prévoit un matage (37) du tourillon de palier (19), du côté frontal et orienté radialement vers l'extérieur, lequel matage (37) recouvre radialement au moins en partie la bague intérieure (22a, 22c, 22e, 22f).
  13. Moteur à combustion interne selon la revendication 1, caractérisé en ce que l'on prévoit au moins deux points de palier (11, 31) pour l'arbre d'entraînement (3a, 3b, 3c, 3f), le deuxième point de palier (31) comprenant un palier à roulement axial (33a à 33c).
  14. Moteur à combustion interne selon la revendication 13, caractérisé en ce que le palier à roulement axial (33b) est réalisé sous forme de roulement à billes disposé dans l'ouverture d'entrée d'arbre (15) du carter de pompe (2), la piste de roulement intérieure pour les billes (38) étant formée par une rainure périphérique (40a) sur une portion d'enveloppe extérieure (39) de l'arbre d'entraînement (3b, 3f) s'étendant dans l'ouverture d'entrée d'arbre (15).
  15. Moteur à combustion interne selon la revendication 1, caractérisé en ce qu'au moins un alésage (30) traversant transversalement l'arbre d'entraînement (3a à 3i) est prévu, lequel débouche dans la région de l'un des points de palier (11) et sert de canal pour lubrifiant.
EP07729697A 2006-06-23 2007-05-31 Pompe à piston Not-in-force EP2035701B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006028851A DE102006028851A1 (de) 2006-06-23 2006-06-23 Kolbenpumpe
PCT/EP2007/055285 WO2007147707A1 (fr) 2006-06-23 2007-05-31 Pompe à piston

Publications (2)

Publication Number Publication Date
EP2035701A1 EP2035701A1 (fr) 2009-03-18
EP2035701B1 true EP2035701B1 (fr) 2010-05-12

Family

ID=38438693

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07729697A Not-in-force EP2035701B1 (fr) 2006-06-23 2007-05-31 Pompe à piston

Country Status (5)

Country Link
US (1) US8256400B2 (fr)
EP (1) EP2035701B1 (fr)
JP (1) JP2009541648A (fr)
DE (2) DE102006028851A1 (fr)
WO (1) WO2007147707A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008000883A1 (de) * 2008-03-31 2009-10-01 Robert Bosch Gmbh Startvorrichtung
DE102008002288B4 (de) * 2008-06-09 2019-08-22 Seg Automotive Germany Gmbh Halteflansch für elektrische Maschine
DE102010022318B4 (de) 2010-06-01 2017-09-07 Schaeffler Technologies AG & Co. KG Rollenstößel
DE102011007458A1 (de) * 2011-04-15 2012-10-18 Schaeffler Technologies AG & Co. KG Radial-Rollenwälzlager
CN103814207B (zh) * 2011-09-09 2016-05-18 爱知机械工业株式会社 燃料泵驱动结构及内燃机
DE102013212047A1 (de) * 2013-06-25 2015-01-08 Robert Bosch Gmbh Pumpvorrichtung, insbesondere Kraftstoffhochdruckpumpvorrichtung für eine Kraftstoffeinspritzeinrichtung
CN106870232A (zh) * 2017-02-07 2017-06-20 无锡开普机械有限公司 发动机高压共轨泵驱动机构
DE102017205200A1 (de) * 2017-03-28 2018-10-04 Robert Bosch Gmbh Pumpe, insbesondere Hochdruckpumpe eines Kraftstoffeinspritzsystems

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4861234A (en) * 1988-09-28 1989-08-29 Allied-Signal Inc. Low-noise pump assembly
US5348382A (en) * 1991-09-30 1994-09-20 Ina Bearing Company, Inc. Anti-lock brake system eccentric bearing arrangement including counterweight
DE4430909A1 (de) 1994-08-31 1996-03-07 Bosch Gmbh Robert Einheit aus Antriebsmotor und Radialkolbenpumpe
DE19650274A1 (de) 1996-12-04 1998-06-10 Teves Gmbh Alfred Pumpenaggregat
DE19650246A1 (de) 1996-12-04 1998-06-10 Bosch Gmbh Robert Von einer Welle eines Verbrennungsmotors angetriebene Kolbenpumpe
DE19712872A1 (de) * 1997-03-27 1998-10-01 Bosch Gmbh Robert Pumpe, insbesonder Hochdruckpumpe für eine Kraftstoffeinspritzvorrichtung eines Verbrennungsmotors
JPH1172014A (ja) * 1997-06-24 1999-03-16 Unisia Jecs Corp 燃料加圧用ポンプ
DE19813322A1 (de) * 1998-03-26 1999-09-30 Itt Mfg Enterprises Inc Motorpumpenaggregat, aufgebaut aus einem Elektromotor und einer von diesem angetriebenen Pumpeneinheit
DE19830890B4 (de) 1998-07-10 2007-06-28 Schaeffler Kg Dreiringnadellagerung für einen Pumpenteil
DE19918020A1 (de) * 1999-04-21 2000-10-26 Continental Teves Ag & Co Ohg Kolbenpumpe und Heizeinrichtung dafür
DE10013269A1 (de) * 2000-03-17 2001-09-20 Continental Teves Ag & Co Ohg Radialkolbenpumpe mit durch eine Dichtlippe gebildetes Ventil
DE10117108A1 (de) * 2001-04-06 2002-10-17 Continental Teves Ag & Co Ohg Motor-Pumpen-Aggregat
DE10208574A1 (de) * 2001-12-01 2003-06-12 Bosch Gmbh Robert Radialkolbenpumpe
US20030145835A1 (en) * 2002-02-05 2003-08-07 Stanadyne Corporation Drive shaft seal for gasoline direct injection pump

Also Published As

Publication number Publication date
DE502007003759D1 (de) 2010-06-24
DE102006028851A1 (de) 2007-12-27
EP2035701A1 (fr) 2009-03-18
JP2009541648A (ja) 2009-11-26
US8256400B2 (en) 2012-09-04
WO2007147707A1 (fr) 2007-12-27
US20110139125A1 (en) 2011-06-16

Similar Documents

Publication Publication Date Title
EP2035701B1 (fr) Pompe à piston
DE19511188C2 (de) Vorrichtung zur Dämpfung von Drehschwingungen in einem Antriebsstrang
DE19580454C1 (de) Wälzlagereinheit mit einer Zentrierung und einem Flansch
DE102014226853A1 (de) Nockenfolgerollenvorrichtung
DE102010054939A1 (de) Lageranordnung für einen Turbolader und Turbolader
WO2007016913A2 (fr) Arbre pourvu de corps fonctionnels, tel qu'un arbre a cames pour moteurs a combustion interne, procedes de fabrication d'arbres de ce type et moteurs a combustion interne equipes de cet arbre
EP0906511B1 (fr) Pompe, notamment pompe a haute pression pour dispositif d'injection de carburant dans un moteur a combustion interne
DE102007025202A1 (de) Lagereinrichtung
DE102004054128A1 (de) Kurbeltrieb
WO2015074649A1 (fr) Dispositif pour faire varier le taux de compression d'une unité de cylindre d'un moteur à combustion interne à piston alternatif
EP1647461A2 (fr) Pompe à piston
DE202005005999U1 (de) Kurbeltrieb
DE102016005644A1 (de) Lagereinrichtung zum axialen Lagern einer Kurbelwelle einer Hubkolbenmaschine
EP1809916A1 (fr) Commande a manivelle
DE19807675A1 (de) Zylinderkopf einer Brennkraftmaschine mit wenigstens einer Nockenwelle
DE102008031578B4 (de) Lageranordnung und Verfahren zu ihrer Montage
EP1174605A2 (fr) Entrainement des auxiliaires d'un moteur à combustion interne
DE20304100U1 (de) Wälzlagervorrichtung und Steuerventil zur Abgasrückführung mit einer solchen Vorrichtung
DE102015201104B3 (de) Oldhamkupplung
DE102013215886A1 (de) Leichtbaudifferenzial mit Schrägrollenlager in O-Anordnung und erhöhter Balligkeit der Laufbahn
DE19542876A1 (de) Wälzlager sowie Verfahren zu dessen Herstellung
DE102013020675A1 (de) Lagerungsanordnung einer Kurbelwelle an einem Kurbelgehäuse einer Hubkolben-Verbrennungskraftmaschine
DE102010020846A1 (de) Nockenwellenlager
WO2007003545A1 (fr) Turbocompresseur pneumatique a suralimentation secondaire
DE102019124040A1 (de) Planetenradlageranordnung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20090123

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

17Q First examination report despatched

Effective date: 20090527

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT SE

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 502007003759

Country of ref document: DE

Date of ref document: 20100624

Kind code of ref document: P

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100531

26N No opposition filed

Effective date: 20110215

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20110407 AND 20110413

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502007003759

Country of ref document: DE

Effective date: 20110214

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502007003759

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER KG, 91074 HERZOGENAURACH, DE

Effective date: 20120828

Ref country code: DE

Ref legal event code: R081

Ref document number: 502007003759

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER KG, 91074 HERZOGENAURACH, DE

Effective date: 20120828

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502007003759

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20140218

Ref country code: DE

Ref legal event code: R081

Ref document number: 502007003759

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20140218

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502007003759

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20150401

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20150730

Year of fee payment: 9

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20160531

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20160531

Year of fee payment: 10

Ref country code: FR

Payment date: 20160531

Year of fee payment: 10

Ref country code: IT

Payment date: 20160523

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502007003759

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161201

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20170531

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170601

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20180131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170531

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170531

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170531

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230522