EP2582929B1 - Rotor de dephaseur d'arbre a cames et dephaseur d'arbre a cames correspondant - Google Patents

Rotor de dephaseur d'arbre a cames et dephaseur d'arbre a cames correspondant Download PDF

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Publication number
EP2582929B1
EP2582929B1 EP11722084.8A EP11722084A EP2582929B1 EP 2582929 B1 EP2582929 B1 EP 2582929B1 EP 11722084 A EP11722084 A EP 11722084A EP 2582929 B1 EP2582929 B1 EP 2582929B1
Authority
EP
European Patent Office
Prior art keywords
rotor
sealing
stator
sealing webs
webs
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
EP11722084.8A
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German (de)
English (en)
Other versions
EP2582929A1 (fr
Inventor
Armin Braun
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co 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 Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2582929A1 publication Critical patent/EP2582929A1/fr
Application granted granted Critical
Publication of EP2582929B1 publication Critical patent/EP2582929B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/356—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear making the angular relationship oscillate, e.g. non-homokinetic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34479—Sealing of phaser devices

Definitions

  • the invention relates to a rotor for a camshaft adjuster with a rotor base body and with a number of arranged on the rotor base body and extending radially outwardly rotor blades. Furthermore, the invention relates to a camshaft adjuster with such a rotor.
  • a rotor serves to support the targeted adjustment of the phase position between a camshaft and a crankshaft in an internal combustion engine. For this purpose, it is usually held as part of a camshaft adjuster in a rotatably connected to the crankshaft stator. When installed, the rotor is rotatably connected to the camshaft and can be adjusted relative to the stator, whereby rotation of the camshaft relative to the stator in a predetermined angular range can be achieved. In this way, for example, specifically the performance of an internal combustion engine can be increased or its fuel consumption can be reduced.
  • the wings of a rotor divided in the installed state usually formed in the stator pressure chambers each in hydraulic areas, which are acted upon to control the camshaft adjuster with hydraulic fluid.
  • functional gaps occur, in particular at the contact point of the rotor blades and the lateral surface of the stator, as a result of which the hydraulic fluid can pass uncontrollably from one to the other hydraulic region.
  • various concepts for sealing are known.
  • a rotor of the aforementioned type is known, which is used in a camshaft adjuster for an internal combustion engine.
  • the rotor has a number of radially oriented vanes, which seal in the region of their end face with respect to the inner circumferential surface of the stator.
  • the sealing element is formed with a U-shaped base cross section with a circumferentially oriented base leg and two radially oriented side legs.
  • the U-shaped base cross-section can embrace the entire end region of the end face of the rotor blade from the outside.
  • Another embodiment provides that the wing has end-side grooves, in which engage the side legs of the separate sealing element.
  • the WO 20061111217 A1 discloses a rotor as part of an apparatus for camshaft adjustment of an internal combustion engine whose rotor body is formed with a number of grooves. In these grooves, the rotor blades are inserted. Between the groove bottom of the groove and the rotor blade here is a separate so-called spring element is arranged, which presses the rotor blade on the one hand radially outward and on the other sealingly abuts the groove bottom. The spring element acts accordingly as a spring and sealing element alike and thus prevents the flow of hydraulic fluid between the hydraulic areas both between the blade end of the rotor blade and in the groove bottom within the rotor body.
  • a vane rotor known as part of a valve timing control apparatus for an internal combustion engine.
  • the wings of the rotor are provided with a cut in the axial direction retaining groove on the end face of the wing tip.
  • a separate sealing element can be fitted, which is in sliding contact with the inner peripheral surface of the stator.
  • the sealing element is additionally held with a leaf spring in the retaining groove of the wing.
  • the DE 198 34 143 A1 discloses a rotor with sealing springs.
  • a second object of the invention is to provide a camshaft adjuster with such a rotor.
  • the first object of the invention is achieved by a rotor for a camshaft adjuster, with a rotor base body and with a number of arranged on the rotor body and radially outwardly extending rotor blades, each having a wing tip. It is provided that the wing ends of the rotor blades are formed to reduce leakage to radially outwardly elastically deformable sealing webs.
  • the invention is based on the recognition that the internal leakage in a camshaft adjuster is caused by gaps that are too wide between the components delimiting the hydraulic areas. To minimize this leakage, the gaps can be reduced such that during operation of a camshaft adjuster sufficient sealing of the hydraulic areas is given from each other. This can be achieved, for example, by narrower gap dimensions to reach. However, in this case a high dimensional accuracy in the manufacture of the components is required to ensure trouble-free operation of the camshaft adjuster. This can only be achieved with great effort up to the present time.
  • the invention surprisingly solves this problem by omitting the use of a separate sealing element.
  • the wing ends of the rotor blades are formed as such for leakage reduction to radially outwardly elastically deformable sealing webs.
  • the sealing webs are part of the rotor blades and fulfill due to their elasticity the required sealing function in the operation of a camshaft adjuster, which was previously taken over by separate sealing elements.
  • the sealing effect of the rotor blades is based, in particular, on the centrifugal forces acting during operation of the internal combustion engine or of the camshaft adjuster, which act on a body in a rotating system.
  • the centrifugal force is directed radially outward from the axis of rotation and depends on the mass of the body and its distance from the axis of rotation.
  • the rotor may be formed, for example, with a substantially circular base body.
  • the number of blades arranged on the main body can be variable depending on the adjustment angle to be set. In principle, it applies here that the more rotor blades are arranged on the rotor base body, the lower is the adjustable adjustment angle.
  • the rotor blades may be attached to the rotor base body as separate components or preferably be made in one piece with this.
  • the rotor blades extend in the radial direction, so that they lie in the installed state with their wing tips on the inner circumference or on the inner circumferential surface of a stator.
  • the wing ends preferably extend with an outer radius corresponding to the inner radius of the stator, in order to avoid, for example, tilting of the wing ends on the inner circumferential surface of the stator during operation.
  • the functionality is ensured due to the elastic deformability of the wing tips.
  • one of the rotor blades may be formed with a locking bore, which serves in the installed state for locking with a stator, so that the stator and rotor can be kept in an optimal position, in particular for the start or idle of an internal combustion engine.
  • the sealing webs can basically be designed differently.
  • the material thickness of the sealing webs is in this case particularly dependent on the overall component nature of the rotor or the rotor blades.
  • the dimensions of the Sealing webs and the material affect the elastic deformability of the sealing webs.
  • the material can be selected correspondingly to the forces acting during operation, so that an adjustment of the resulting radial leakage gaps between the wing tips and the inner circumferential surface of a stator is possible both at standstill and during operation.
  • the webs are formed in particular by a targeted material weakening at the wing tip.
  • material recesses are introduced in the wing tips to form the sealing webs.
  • the material recesses are in this case preferably limited in the radial direction of the sealing webs.
  • the material recesses can be introduced, for example, as cavities, as recesses or depressions in the rotor blades. They are preferably already introduced into the rotor blades during the immediate production of the rotor, for example in the case of a sintered or cast part by the use of a corresponding shape, so that no subsequent processing steps are necessary.
  • the elastic sealing webs can be designed durable by a vote of the material recesses with the material thickness, so that they can always withstand the forces acting on them resistant.
  • the material recesses are formed on the wing tips along the circumferential direction with a constant radial width.
  • a uniform sealing effect occurs over the circumference.
  • the highest sealing effect is achieved in the middle of the web, since the elastic deformation is most pronounced at this point.
  • the material recesses are at the wing tips along the circumferential direction with a variable radial Width trained. This results in a varying material thickness along the circumferential direction, whereby the elastic deformability can be specifically adapted to the requirements. In particular, this creates a local deformation or bending area for the sealing webs.
  • the material recesses defining at the wing ends sealing webs are formed with a freely movable web end. Since the web is firmly connected only on one side with the wing end, in this case the freely movable end can be easily elastically deformed during operation. This embodiment also makes it possible to influence the width of the radial leakage gaps along the circumferential direction.
  • the rotor body is made with the rotor blades in one piece with a powder metallurgy process.
  • the one-piece production is particularly advantageous because a simplification of the manufacturing process can be achieved.
  • the invention makes it possible to manufacture rotor body and rotor blades as a component in a common process to provide the density functionality. An assembly of individual parts is eliminated. In contrast to a multi-part manufacturing additional possible leaks are avoided at the contact point of Rotorgrundköpers with the rotor blades.
  • a sintering method is particularly preferred.
  • a sintering process can achieve a high precision, which is advantageous for the adjustment of the radial leakage gaps. Since sintered components have a high dimensional accuracy, additional elaborate post-processing steps of the rotor can be omitted.
  • a sintering process additionally offers the Possibility of using an automated process flow, which avoids increased process costs and additional processing effort.
  • the sintered material has an influence on the strength and the weight of the rotor, which in turn can affect the elastic deformation of the sealing webs. Accordingly, the choice of sintering material can also influence the remaining width of the radial leakage gaps in the operation of a camshaft adjuster.
  • the sealing webs may have a wall thickness, through which the desired sealing effect is given at a sufficiently high strength.
  • the wall thickness in this case depends in the circumferential direction on the shape of the material recesses formed in the wing ends. For example, the wall thickness of a dumbbell-shaped material recess at the outer ends of the sealing webs, in the region of the larger recesses, less than in the intervening area.
  • the second object of the invention is achieved by a camshaft adjuster for an internal combustion engine, comprising a stator and disposed within the stator, relative to this rotatable rotor according to the aforementioned embodiments. It is provided that the sealing webs of the radially outwardly extending wing ends seal against the inner circumferential surface of the stator.
  • the sealing effect of the sealing webs is based on the centrifugal forces acting during operation of the camshaft adjuster.
  • the sealing webs are radially elastically deformed and pressed against the inner circumferential surface of the stator. This results in a reduction of the radial leakage gaps between the rotor blades and the inner wall of the stator.
  • the sealing effect achieved thereby allows the operation of a camshaft adjuster without an additional sealing element.
  • the stator usually has a number of radially inwardly extending webs, between which pressure chambers are formed.
  • the radially outwardly extending wings of the rotor can be positioned, so that each of the outer sides of the wings, the hydraulic areas for pressurization with hydraulic fluid.
  • To act on the rotor in particular oil passages in its base body, can be pumped through the oil in the pressure chambers of the stator or the camshaft adjuster.
  • At the webs of the stator wing stop surfaces may be formed, which can strike the wings of a rotor in the installed state.
  • the camshaft adjuster is usually formed next to the stator and the rotor still with a sealing cover and with a locking cover.
  • the locking cover is preferably connected to the stator and limits the pressure chambers camshaft side. It serves to seal the pressure chamber to the outside, prevents uncontrolled leakage of hydraulic fluid and thus reduces external leakage.
  • a gate is formed, which serves to lock the stator and rotor in a designated position.
  • the gap dimensions decrease as a function of the centrifugal forces acting on the rotor or on the wing ends.
  • the dimensions or the width of the radial leakage gaps here depend, for example, on the component thickness of the rotor and on the wall thickness of the sealing webs. These and the material recesses can be matched to each other, so that a durable design of the elastic or elastically deformable sealing webs is possible.
  • FIG. 1 to 3 in each case a rotor with differently shaped rotor blades in a cross section and Fig. 4 a camshaft adjuster with a rotor according to Fig. 1 when installed in a cross section.
  • Fig. 1 shows a rotor 1 for a phaser in a cross section.
  • the rotor 1 has a rotor base body 3 with four radially outwardly extending rotor blades 5.
  • the rotor blades 5 serve to divide a respective pressure chamber of a camshaft adjuster into two adjacent hydraulic areas.
  • a camshaft adjuster is in Fig. 4 shown.
  • the rotor base body 3 and the rotor blades 5 are manufactured in one piece by a sintering process from a metallic material.
  • a sintering process offers the possibility of using an automated process flow and is therefore inexpensive and easy to carry out. Due to the dimensional accuracy of the method, the rotor 1 can be made so that the radial leakage gaps between the wing tips and the inner circumferential surface of a stator when installed are sufficiently low.
  • the rotor blades 5 have wing tips 7, which are designed to reduce the leakage in a camshaft adjuster.
  • the wing tips 7 are formed to radially outwardly elastically deformable sealing webs 9. They persist made of the same material as the rotor blades 5 and are produced during the sintering process as part of the rotor blades 5 or as part of the rotor 1.
  • the elastic deformability of the sealing webs 9 is caused by the introduced in the wing ends 7 material recesses 11.
  • the material recesses 11 are limited in the radial direction of the sealing webs 9 and extend in the circumferential direction with a constant radial gap. As a result, a uniform sealing effect occurs over the circumference during operation. In the middle of the sealing webs 9 in this case the highest sealing effect is achieved, since at this point the elastic deformation of the blade ends 7 is most pronounced.
  • the material recesses 11 are already introduced directly into the rotor blades 5 by the manufacturing method of the rotor 1.
  • a locking bore 13 is included for locking with a stator in the installed state.
  • a piston for example, engage a piston through the locking hole 13 in a slot in the bottom of a locking lid, so that the rotor 1 and a stator can be kept in an optimal position, in particular for the start or idle of an internal combustion engine.
  • the backdrop to the lock is in Fig. 4 to see.
  • a rotor 21 for a phaser in a cross section to see.
  • the rotor 21 also has a rotor main body 23 with four radially outwardly extending rotor blades 25, which divide the pressure chambers of a camshaft adjuster into hydraulic regions when installed.
  • the rotor 21 is also made in one piece by means of a sintering process of a metallic material.
  • sealing webs 31 In the wing ends 27 material recesses 29 are also introduced, which are bounded radially outwardly by sealing webs 31.
  • the material recesses 29 are formed with a circumferentially extending variable radial gap in the form of a dumbbell. Accordingly, the sealing webs 31 have a wall thickness changed along the circumferential direction. Their name 33, 35 is shown for clarity only on a material recess 29. At the circular recesses 33 a deformation point for the elastic movement of the sealing web 31 is created specifically to the outside.
  • FIG. 1 is also of a rotor blade 25 of the rotor 21 comprises a locking bore 37 for locking with a stator in the installed state.
  • Fig. 3 also shown in a cross section rotor 41 with a rotor base 43 and four arranged on this rotor blades 45 is corresponding to the Fig. 1 and 2 manufactured in one piece by sintering.
  • the radially outwardly extending rotor vanes 45 have at the wing ends 47 sealing webs 49.
  • sealing webs 49 limit the material recesses 51 introduced into the wing ends 47 in the radial direction.
  • the material recesses 51 are formed in the circumferential direction with a variable radial gap and opened to one of the wing stop surfaces 71, 73 out.
  • the wing ends 47 are weakened by the material recesses 51 on one side to be hinged sealing webs 49.
  • the respective free web end 53 of the sealing webs 49 is pressed radially outward by the centrifugal force acting on the rotor 41 during operation.
  • the wall thickness at the location of the circular recess 57 is increased relative to the location of the adjoining web-shaped recess 57.
  • Their designation 55, 57 is as in Fig. 2 for the sake of clarity only shown on a material recess 51.
  • a locking hole 59 is introduced, which serves in the installed state, the locking of the rotor and stator in a desired position.
  • Fig. 4 shows a camshaft adjuster 61 with a rotor used in a stator 63 according to FIG Fig. 1 in a top view.
  • the rotor 1 has a rotor main body 3 with four rotor blades 5 extending radially outwards.
  • Rotor main bodies 3 and rotor blades 5 are produced in one piece by sintering from a metallic material. For the description of the rotor 1 is at this point Fig. 1 directed.
  • the stator 63 has radially inwardly extending webs 65, between each of which a rotor blade 5 of the rotor 1 is positioned.
  • the rotor blades 5 divide the pressure chambers 67 formed in the stator 63 into two hydraulic areas 69, which are located on the right or left of the rotor blades 5, respectively. This is in Fig. 4 due to the clarity of only one pressure chamber 67 or two hydraulic areas 69 indicated.
  • wing stop surface 71, 73 is formed, which stop the rotor blades 5 in a certain position by a stop. Both wing stop surfaces 71, 73 are located within a pressure chamber 67 or respectively in a hydraulic region 69, so that the rotor blade 5 can abut the pressure chamber 67 on both sides.
  • Fig. 4 shows the camshaft adjuster 61 at a standstill, wherein the radially outwardly extending wing ends 7 of the rotor vanes 5, and the sealing webs 9 with its outer periphery do not rest directly on the inner circumference of the stator 63.
  • the radial leakage gaps 75 which are formed between the inner circumferential surface 77 of the stator 63 and the blade ends, can therefore be clearly seen.
  • the leakage gaps 75 decrease while increasing the tightness between the hydraulic regions 69.
  • the sealing webs 9 are deformed radially in the direction of the inner circumferential surface 77 of the stator 63, so that the radial Reduce the gap between rotor 1 and stator 63.
  • the leakage is reduced and a sealing of the hydraulic regions 69 from each other can be achieved without the use of separate sealing elements.
  • the rotor 1 has oil passages for pressurizing the pressure chambers 67 with oil, wherein these passages can not be recognized, since they are located inside the body of the rotor 1.
  • a locking bore 13 is introduced, through which a piston, not shown, can engage in the introduced in the locking cover 79 slide 81.
  • the rotor 1 can be held in a predetermined position.
  • the piston is raised and the rotor 1 can move in a certain adjustment angle.
  • the locking cover 79 is connected to the stator 63 and limits the pressure chambers 67 camshaft side. In this way, the locking lid 79 additionally serves to reduce the external leakage of the camshaft adjuster 61.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (8)

  1. Rotor (1, 21, 41) pour un déphaseur d'arbre à cames (61), comprenant un corps de base de rotor (3, 23, 43) ainsi qu'un certain nombre de pales de rotor (5, 25, 45) disposées sur le corps de base de rotor (3, 23, 43) et s'étendant radialement vers l'extérieur, lesquelles comprennent respectivement une extrémité de pale (7, 27, 47), caractérisé en ce que les extrémités de pale (7, 27, 47) des pales de rotor (5, 25, 45) sont formées de manière à former des nervures d'étanchéité (9, 31, 49) déformables élastiquement radialement vers l'extérieur en vue de la réduction des fuites.
  2. Rotor (1, 21, 41) selon la revendication 1, caractérisé en ce que des évidements de matériau (11, 29, 51) sont ménagés dans les extrémités de pale (7, 27, 47) pour réaliser les nervures d'étanchéité (9, 31, 49).
  3. Rotor (1, 21, 41) selon la revendication 2, caractérisé en ce que les évidements de matériau (11, 29, 51) aux extrémités de pale (7, 27, 47) sont délimités dans la direction radiale par les nervures d'étanchéité (9, 31, 49).
  4. Rotor (1, 21, 41) selon la revendication 2 ou 3, caractérisé en ce que les évidements de matériau (11, 29, 51) aux extrémités de pale (7, 27, 47) sont réalisés de manière à présenter une largeur radiale constante le long de la direction périphérique.
  5. Rotor (1, 21, 41) selon la revendication 2 ou 3, caractérisé en ce que les évidements de matériau (11, 29, 51) aux extrémités de pale (7, 27, 47) sont réalisés de manière à présenter une largeur radiale variable le long de la direction périphérique.
  6. Rotor (1, 21, 41) selon la revendication 3, caractérisé en ce que les nervures d'étanchéité (9, 31, 49) délimitant les évidements de matériau (11, 29, 51) aux extrémités de pale (7, 27, 47) sont réalisées de manière à présenter une extrémité de nervure (53) librement mobile.
  7. Rotor (1, 21, 41) selon l'une quelconque des revendications précédentes, caractérisé en ce que le corps de base de rotor (3, 23, 43) est produit d'une seule pièce avec les pales de rotor (5, 25, 45) à l'aide d'un procédé de la métallurgie des poudres.
  8. Déphaseur d'arbre à cames (61) pour un moteur à combustion interne, comportant un stator (63) ainsi qu'un rotor (1, 21, 41), disposé à l'intérieur du stator (63) et pouvant tourner par rapport à celui-ci, selon l'une quelconque des revendications 1 à 7, les nervures d'étanchéité (9, 31, 49) des extrémités de pale (7, 27, 47) s'étendant radialement vers l'extérieur réalisant l'étanchéité par rapport à la surface d'enveloppe intérieure (77) du stator (63).
EP11722084.8A 2010-06-17 2011-05-31 Rotor de dephaseur d'arbre a cames et dephaseur d'arbre a cames correspondant Not-in-force EP2582929B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010024197A DE102010024197A1 (de) 2010-06-17 2010-06-17 Rotor für einen Nockenwellenversteller und Nockenwellenversteller
PCT/EP2011/058879 WO2011157542A1 (fr) 2010-06-17 2011-05-31 Rotor pour déphaseur d'arbre à cames et déphaseur d'arbre à cames correspondant

Publications (2)

Publication Number Publication Date
EP2582929A1 EP2582929A1 (fr) 2013-04-24
EP2582929B1 true EP2582929B1 (fr) 2014-07-16

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EP11722084.8A Not-in-force EP2582929B1 (fr) 2010-06-17 2011-05-31 Rotor de dephaseur d'arbre a cames et dephaseur d'arbre a cames correspondant

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Country Link
US (1) US8635978B2 (fr)
EP (1) EP2582929B1 (fr)
CN (1) CN102947553B (fr)
DE (1) DE102010024197A1 (fr)
WO (1) WO2011157542A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012213176B4 (de) * 2012-07-26 2021-07-01 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller
DE102013209520A1 (de) 2013-05-23 2014-12-11 Schaeffler Technologies Gmbh & Co. Kg Rotor für einen Flügelzellenversteller einer Nockenwellenverstelleinrichtung
JP6942803B2 (ja) * 2017-01-03 2021-09-29 ジーケーエヌ シンター メタルズ、エル・エル・シー ロータ及び研削加工のために均等化された表面積を有するロータの製造方法

Family Cites Families (7)

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Publication number Priority date Publication date Assignee Title
US6263843B1 (en) 1998-03-25 2001-07-24 Unisia Jecs Corporation Valve timing control device of internal combustion engine
DE19834143B4 (de) * 1998-07-29 2014-03-20 Schaeffler Technologies AG & Co. KG Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Nockenwellenverstelleinrichtung mit Flügelrad
DE10356907A1 (de) * 2003-12-02 2005-07-07 Hydraulik-Ring Gmbh Nockenwellenverstelleinrichtung für Verbrennungskraftmaschinen von Kraftfahrzeugen
DE102005017436A1 (de) 2005-04-15 2006-10-19 Schaeffler Kg Vorrichtung zur Nockenwellenverstellung einer Brennkraftmaschine
DE102006004718A1 (de) 2006-02-02 2007-08-23 Schaeffler Kg Nockenwellenversteller in Flügelzellenbauweise
DE102006022219B4 (de) * 2006-05-11 2008-01-03 Hydraulik-Ring Gmbh Leckagedichter Nockenwellenversteller mit Rückstellfeder
US7878164B2 (en) * 2006-12-13 2011-02-01 Delphi Technologies, Inc. Apparatus for preventing leakage across rotor vanes in a vane-type camshaft phaser

Also Published As

Publication number Publication date
CN102947553B (zh) 2015-02-11
CN102947553A (zh) 2013-02-27
DE102010024197A1 (de) 2011-12-22
WO2011157542A1 (fr) 2011-12-22
EP2582929A1 (fr) 2013-04-24
US8635978B2 (en) 2014-01-28
US20130081585A1 (en) 2013-04-04

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