WO2016165699A1 - Déphaseur d'arbre à cames comprenant un élément de précontrainte axial - Google Patents

Déphaseur d'arbre à cames comprenant un élément de précontrainte axial Download PDF

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Publication number
WO2016165699A1
WO2016165699A1 PCT/DE2016/200083 DE2016200083W WO2016165699A1 WO 2016165699 A1 WO2016165699 A1 WO 2016165699A1 DE 2016200083 W DE2016200083 W DE 2016200083W WO 2016165699 A1 WO2016165699 A1 WO 2016165699A1
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WO
WIPO (PCT)
Prior art keywords
rotor
camshaft
distal end
axial
adjuster
Prior art date
Application number
PCT/DE2016/200083
Other languages
German (de)
English (en)
Inventor
Holger BRENNER
Original Assignee
Schaeffler Technologies AG & 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 & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2016165699A1 publication Critical patent/WO2016165699A1/fr

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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
    • F01L1/3442—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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • 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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location oil control valves
    • 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
    • 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
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
    • 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
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/04—Camshaft drives characterised by their transmission means the camshaft being driven by belts
    • 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
    • F01L2301/00—Using particular materials
    • 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
    • F01L2303/00—Manufacturing of components used in valve arrangements

Definitions

  • the invention relates to a camshaft adjuster with a radially arranged within a stator rotor which is rotatable relative to the stator, wherein the rotor is prepared to be rotatably connected to a camshaft and having a radially inner rotor surface with at least one rotor form-fitting element, wherein the rotor form-fitting element is prepared to enter into a torque-transmitting positive fit with a corresponding camshaft form-locking element.
  • the published patent application DE 10 2010 046 619 A1 discloses a rotor for a camshaft adjuster and a camshaft adjusting system.
  • a rotor for a camshaft adjuster with a substantially annular rotor base body, which has an end face for axial connection to a camshaft.
  • the publication relates to a camshaft adjusting system with such a rotor.
  • a device for variably setting the control times of gas exchange valves of an internal combustion engine comprising a drive element and an output element and a camshaft, wherein an axial side surface of the camshaft rests against an axial side surface of the output element, wherein on one of the adjacent axial soflä- Chen a form-fitting element for aligning the output element is provided on the camshaft with respect to the circumferential direction, which engages in a Gegenform gleich- element of the other component.
  • the published patent application DE 101 34 320 A1 is also located in this field. It discloses a device for changing the timing of gas exchange valves of an internal combustion engine, in particular of Rotationskolbenverstell Surpriseen for Deckelwinkelver ein a camshaft relative to a crankshaft.
  • the region of the power cone of the fastening screw on the output unit as a separate, consisting of a tiknapssfes- th material and at the same time provided as a prefabricated pressure medium distributor of the device sleeve is formed on the output unit axially and radially and circumferentially form and / or non-positively lockable and deformation-free screwed to the camshaft.
  • European patent application EP 1 471 215 A2 discloses a camshaft adjuster for vehicles.
  • the device disclosed therein is characterized in that the camshaft has at least one form and / or force-locking part on which the rotor is non-rotatably seated with a base body having a different diameter than a circle circumscribing the cams of the camshaft.
  • the invention is in the field of internal combustion engines, particularly hydraulic and electric camshaft adjusters for chain and belt drives for both gasoline and diesel engines, and also applications for concentric camshaft phasers.
  • the known prior art usually describes such camshaft adjuster, which are fastened with a central screw on the camshaft.
  • connection technique which is based on a frictional connection by a screw connection.
  • a biasing force is applied in the axial direction.
  • a tangential operating force to be transmitted. Since a coefficient of friction acts between the axial force and the tangential force, a very high axial force must be applied in order to transmit the required tangential force. Due to this high axial force, the parts in the clamping assembly are heavily loaded and partially deformed. These deformations have negative effects on the centering accuracy and leakage gaps between the components involved, such as the rotor internal geometry and the central valve.
  • a central valve for screwing the adjuster to the camshaft, the angular position of the radial bores in the assembled state is not defined.
  • the radial bores which guide the oil to the outside, are in different angular positions. Therefore, this angular position does not specifically in the continuing radial bores of the rotor, as they are in turn in any angular position to the valve. If the radial bores of the valve and the rotor are not aligned, this is detrimental to the oil supply to the pressure chambers.
  • an annular channel must be created in the rotor, which is associated with increased flow losses and has a slower response of the adjustment system result.
  • the ring channels in the rotor mean a more complex production process and a larger radial space of the rotor.
  • the complex design of the central valve as a screw is to be avoided.
  • This screw housing must withstand high mechanical loads (preload force and bolting torque) and must therefore be stably constructed.
  • This extra housing also obstructs the flow of oil. If this housing is omitted, the valve can be made smaller and optimal in terms of the oil flow.
  • the assembly inside the camshaft is simpler and can e.g. be realized by a locking ring.
  • the disadvantages of the prior art are, inter alia, also the fact that the assembly of the camshaft adjuster on the camshaft only by means of very low Manufacturing tolerances and a high assembly cost can be performed so that the camshaft adjuster assumes the intended position relative to the camshaft.
  • a disadvantage of the known devices is that the assembly is very time consuming. Furthermore, with the existing devices assembly errors can not be completely avoided.
  • the rotor form-fitting elements extend in the axial direction over the entire rotor inner surface.
  • the rotor form-fitting elements have a surface which is large enough to realize the positive connection necessary for the torque transmission.
  • the device allows to reliably transmit the forces and moments occurring in an axially limited space.
  • a proximal end face is formed / provided at a proximal end of the rotor and is adapted to be in contact with the biasing element.
  • the proximal end face can also be designed in such a way that it optimally absorbs the introduction of force, which it experiences from the side of the pretensioning element.
  • the proximal end side is thus made possible to tailor-made with regard to the choice of materials and the surface finish on their application.
  • the biasing element is configured as a plate spring and the biasing element is such that it is in contact with the camshaft at its proximal end and is in contact with the rotor at its distal end.
  • the biasing member is in contact with both the camshaft and with the rotor, it allows an axial bias of the two components relative to each other.
  • the proximal end is connected to the camshaft and the distal end is in communication with the rotor, since the biasing member is mounted in time before the camshaft adjuster.
  • a distal end portion has a shaft shoulder which is directed radially outward, wherein the shaft shoulder is arranged at such an axial position that in the direction of the distal end of the camshaft, a sufficiently long portion is formed to it preferably to arrange the rotor and the biasing element without overhang.
  • rotor fluid passages are arranged inside the rotor, which lead from the rotor inner surface to a rotor outer surface and are intended to transport a hydraulic fluid and / or that the distal end portion has camshaft fluid passages which extend radially and which are suitable for this purpose to transport a hydraulic fluid, in particular, they are aligned with the rotor fluid channels.
  • This continuous connection first from the rotor inner surface to the rotor outer surface allows the supply of the fluid chambers with hydraulic fluid, preferably hydraulic oil, whereby an efficient operation of the camshaft adjuster is ensured.
  • the arrangement of the rotor fluid channels within the rotor causes a minimal axial space of the camshaft adjusting unit.
  • camshaft fluid ducts By means of the camshaft fluid ducts it is also made possible to supply the fluid chambers of the camshaft adjuster through the camshaft with hydraulic fluid, whereby the function of the camshaft adjuster is ensured. With ensured strength of the camshaft, it is thus possible to keep the necessary space minimal because the fluid channels that supply the hydraulic chambers with fluid within the camshaft are arranged.
  • a further advantageous embodiment is that an angular orientation between the rotor and the camshaft is made via the positive locking. This makes it possible to perform a centering without additional effort. This minimizes the installation space and above all the costs to be incurred, since no extra component for angle orientation is necessary.
  • a further advantageous embodiment is that at least six rotor form-fitting elements are mounted on the rotor inner surface in the circumferential direction.
  • This arrangement with six rotor form-fitting elements makes it possible to transmit the high torques occurring by means of a positive connection from the camshaft adjuster to the camshaft.
  • the number of six rotor form-fitting elements has the advantage of resulting in a symmetrical arrangement, which is an advantage in terms of manufacturing cost due to the complexity.
  • the rotor form-fitting elements are designed as indentations which are directed radially outward. These indentations are suitable for protrusions which are attached to the camshaft projecting into them.
  • the recesses are designed so that their height is sufficiently large to transmit the forces and moments occurring. Thus, a functional true fit is possible with minimal axial and radial space.
  • a further advantageous embodiment is characterized in that the rotor form-locking elements extending in the axial direction each have two side edges, wherein the first side edge is aligned in the direction of a circumferential direction and the second side edge is oriented in the direction of the opposite circumferential direction, wherein the distance in Circumferential direction between the first side edge and the second side edge is small compared to the axial length of the rotor form-fitting element. It follows that the recesses, which are defined by the side edges, leave in their interstices in the circumferential direction so much space available that the rigidity of the rotor is not impaired, whereby this can continue to fulfill its function in an optimal manner.
  • first side flank and the second side flank are configured in such a way that centering of the rotor relative to the camshaft can be performed via them. This centering allows only a relative position of the rotor to the camshaft, whereby the assembly is simplified on the one hand, and on the other a faulty mounting is avoided. This decrease in the degree of complexity of the assembly entails not negligible cost advantages in the assembly.
  • the rotor is made of sintered steel.
  • the rotor can be manufactured with a high degree of geometrical accuracy while continuing to meet the requirements of the material in terms of its strength. Widely used sintering techniques can be used, thereby reducing manufacturing costs.
  • the rotor is mechanically recompressed. This causes an increase in the strength of the rotor made of sintered steel. Thus, even the highest torques can be transmitted through the rotor to the camshaft, without the material being adversely affected.
  • a further advantageous embodiment is characterized in that an insertion phase is arranged on the proximal end face of the rotor for simplifying the assembly. This optimizes the assembly process, further reducing the complexity of the assembly. In addition, such an insertion phase minimizes the risk of incorrect installation.
  • the diaphragm spring is punched from spring steel and then formed. In this way, conventional manufacturing methods for the diaphragm spring can continue to be applied, whereby the existing expertise can also be used for the disc spring now installed in this unit. Development costs for the preparation of a new diaphragm spring thus eliminated.
  • the plate spring is reworked by means of a heat treatment.
  • This post-processing ensures that the plate spring can apply the necessary forces for the axial form-fit or the axial preload.
  • the heat treatment guarantees a long life of the diaphragm spring.
  • the standardized process of heat treatment also keeps the effort required to a minimum.
  • Another embodiment with advantageous properties is characterized in that the biasing element has a contact area and the contact area forms rounded edges. By means of this rounding off, wear is avoided, which has a positive effect on the maintenance intervals and the service life of the camshaft adjuster. In addition, chips generated during operation are thus avoided due to excessive frictional forces, which has a positive effect on the operating temperature and does not result in undesired friction bodies.
  • a further advantageous embodiment is characterized in that the pretensioning element is work hardened by means of shot peening. This strain hardening optimizes the preload force that the biasing element can apply, thereby optimally performing the axial preload of the phaser relative to the camshaft.
  • the pretensioning element is configured by means of two disk springs placed opposite one another, thereby avoiding an abutment region lying obliquely against the rotor. The resulting from the oblique system inefficient power transmission is thus bypassed, whereby the initiated by the biasing element form-fitting is optimally designed.
  • the biasing element has a progressive spring characteristic. This has the effect that under high load a penetration of the spring is prevented, while in the range of the normal load, a soft comfortable suspension is realized. In this way, it is possible that the biasing element causes a force adapted to the operating state.
  • the biasing element is designed as a compression spring. This is very low in their production, resulting in decreasing production costs of the unit. Furthermore, compression springs have long lifetimes, which is not expected to be a maintenance of the spring.
  • the biasing element is designed as a rubber buffer.
  • This has a very low density, resulting in a weight reduction of the unit, which increases the efficiency of the unit.
  • a rubber buffer has damping properties, which may well be desirable for the vibrations occurring in the engine. Rubber buffers are also preferred to form progressive spring characteristics. With their low production costs, rubber buffers also represent an advantage in terms of cost-effectiveness.
  • the biasing element has a central through hole which exceeds the diameter of the diameter of the camshaft in diameter. On the- This ensures that the preload element can be easily mounted on the camshaft. Any wedges are also avoided, which avoids undesirably high assembly times.
  • a further advantageous embodiment is characterized in that the biasing element is designed such that it exerts a purely axial force on the rotor in the direction of the distal end. In this way, a positive connection is made possible by means of the fastened at the distal end fastener without loss of power. The effect of the force in the axial direction also prevents unwanted bending moments from occurring within the components concerned, which would have a negative effect on the service life of the individual parts.
  • the camshaft when the camshaft is such that it has a distal end portion which is in contact with the rotor at its radial outer lateral surface.
  • the separate design of such an end section causes it to be such that it optimally fulfills the requirements imposed on it. Due to the geometric separation of the torque transmitting portion, so the distal end portion to the rest of the camshaft, these two have separate material properties, whereby both are able to fulfill their function satisfactorily with the least possible cost of materials. This separation of the function of the individual sections of the camshaft causes the camshaft is designed with the greatest possible efficiency. So it is advantageous if the distal end portion is formed as a hollow shaft.
  • This hollow shaft makes it possible to supply the camshaft adjuster via the radially inner part of the camshaft with hydraulic fluid.
  • the space is used optimally in this way, since no external fluid channels are necessary. It is also advantageous if the outer diameter of the distal end portion exceeds the outer diameter of the proximal, remaining camshaft. In this way, the distal end portion is caused to have a sufficiently high area moment of inertia, thereby ensuring that despite the configuration as Hollow shaft sufficient force transmission takes place. The radially required space is thus kept minimal.
  • a further advantageous embodiment is characterized in that the distal end section has an annular groove which is suitable for arranging the axial delimiting element therein.
  • the position of the limiting element is clearly defined, which entails a geometric determination of the camshaft adjuster in the axial direction.
  • the axial fixing of the delimiting element by means of an annular groove causes the axial delimiting element can be conveniently attached, without the need for a shaft shoulder, which would increase the radial space.
  • an insertion phase is arranged at the distal end of the camshaft to simplify the assembly. Characterized in that thus given the opportunity to center the camshaft adjuster also on the camshaft, the flexibility of the arrangement is increased. The resulting simplified assembly has a positive effect on the required assembly time and thus the production costs.
  • the camshaft has at least six camshaft form-locking elements in the circumferential direction on a camshaft outer surface.
  • the number of camshaft form-locking elements should correspond to the number of rotor form-fitting elements, which enables an optimal positive locking.
  • camshaft form-locking elements extend in the axial direction as long as the rotor form-fitting elements. In this way it is possible that no axial space is wasted and yet the force necessary for the positive connection is transmitted functionally filling.
  • camshaft form-locking elements are formed as projections which are directed radially outward. These projections it is possible to intervene geometrically determined in the previously described indentations of the rotor.
  • An advantageous embodiment is also characterized in that the camshaft form-locking elements are in engagement with the rotor-form-fitting elements, whereby the torque-transmitting form-fit comes about, wherein the rotor form-fitting element and the camshaft form-fitting element each have a height in the radial direction, this height does not have to be identical and the engagement between the rotor form-fitting element and the camshaft closure element is designed such that it extends at least over 70% of the flank height of the positive-locking element with the lower height, ie has an engagement ratio of at least 0.7.
  • This engagement ratio ensures sufficient power transmission, while at the same time the space situation is taken into account. Too high engagement ratios are avoided, which resulted in very high manufacturing tolerances and thus increased the cost in height. Furthermore, the risk of geometric over-determination of the arrangement, which would entail an engagement ratio of 1, banned.
  • This aligned arrangement makes it possible that no annular channel must be created in the rotor, resulting in a less flow losses and also keeps the production costs low, since this arrangement is much easier to implement.
  • this arrangement also causes the response of the adjustment system to changes in hydraulic fluid pressure to be extremely fast, as the fluid travels little distance from the hydraulic tank into the fluid chamber.
  • a further advantageous embodiment is that the rotor fluid channels are arranged in the region of the rotor form-fitting elements.
  • a further advantageous embodiment is characterized in that the camshaft fluid channels are arranged in the region of the camshaft form-fitting elements. It is thus guaranteed that the camshaft fluid ducts are aligned with the rotor fluid ducts, since it is ensured with the above-described inventive features according to the invention that the rotor form-locking elements and the camshaft form-locking elements interlock. It is also advantageous if the rotor fluid ducts and / or the camshaft fluid ducts are arranged in the region of an axially extending edge of one of the sections which form the form-locking connection or adjoin it. They can thus be arranged in a radially inwardly projecting nose region of the rotor or adjacent to a radially outwardly protrudingberichtur of the camshaft, for example in the region of a depression of the camshaft.
  • a further advantageous embodiment is characterized in that zero, one, two or more rotor fluid passages run radially per rotor form-fitting element. With This number of radially extending rotor channels per Rotorform gleichelennent is guaranteed that each hydraulic chamber of the rotor via one channel hydraulic fluid to another and discharged via another channel hydraulic fluid. It is also advantageous if the camshaft fluid channels are such that they can be connected at their radially inner end with a central valve. In this way, a reliable oil supply of the camshaft fluid ducts and thus also the rotor fluid ducts and the hydraulic chambers of the camshaft adjuster is guaranteed. A functional work of the camshaft adjuster is thus ensured.
  • a leakage gap is formed between the flanks of the rotor form-fitting elements and the flanks of the camshaft form-fitting elements, which can be filled with oil.
  • an active oil lubrication of the camshaft adjuster is realized, which eliminates the additional expense that normally has to be applied for oil lubrication.
  • the inventive solution of the problem is the connection of the camshaft adjuster by an axially biased form-fit.
  • the positive connection is the power transmission of the camshaft torque and can be realized in the form of a spline, splined shaft, keyway or polygon connection.
  • the device according to the invention also has an additional spring element between the rotor and the camshaft, which exerts a force in the axial direction and thus compensates for the axial play occurring after assembly. Furthermore, an additional form element is included, which projects radially into the camshaft and fixes the axial position of the rotor to the camshaft.
  • Fig. 2 is a longitudinal section of the entire unit along the line II-II of Fig. 1 and
  • Fig. 3 is a plan view of the entire unit
  • Fig. 4 shows a perspective view of the rotor together with its rotor fluid ducts
  • Fig. 5 is a perspective view of the camshaft, together with their camshaft fluid channels.
  • a camshaft adjuster 1 which has a radially arranged inside a stator 2 rotor 3, wherein the rotor 3 is rotatable relative to the stator 2.
  • the rotor 3 is prepared to be rotatably connected to a camshaft 4. It also has a radially inner rotor surface 5, which comprises at least one rotor form-fitting element 6.
  • the rotor form-fitting element 6 is prepared to enter into a torque-transmitting positive connection with a corresponding camshaft form-fitting element 7, as is clear from the summary of FIGS. 4 and 5.
  • Fig. 2 shows a biasing member 8, which rests on the rotor 3, that the positively locking elements of the rotor 3 and the camshaft 4 are biased against each other at least in the axial direction / braced.
  • the positive connection is configured as a splined connection. Here protrude six projections 15 of the camshaft 4 in six indentations 16 of the rotor.
  • the distal end portion 14 of the camshaft 4 is configured as a hollow shaft.
  • the rotor fluid ducts 13 arranged therein are located at different positions both in the circumferential direction and in the axial direction.

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

Abstract

L'invention concerne un déphaseur d'arbre à cames (1) comprenant un rotor (3) disposé de manière radiale sous un stator (2), lequel peut tourner par rapport au stator (2). Le rotor (3) est préparé pour être relié de manière solidaire en rotation à un arbre à cames (4), et il comporte une surface intérieure de rotor (5) située radialement à l'intérieur, pourvue au moins d'un élément à complémentarité de forme de rotor (6). L'élément à complémentarité de forme à rotor (6) est préparé pour adopter, avec un élément à complémentarité de forme d'arbre à cames (7) correspondant, une complémentarité de forme à transmission de couple de rotation. Un élément de précontrainte (8) repose sur le rotor (3) de telle manière que les éléments sous complémentarité de forme du rotor (3) et de l'arbre à cames (4) sont précontraints les uns par rapport aux autres dans une direction axiale. L'invention concerne également un système de déphasage (25) comprenant un déphaseur d'arbre à cames (1) et un arbre à cames (4), la liaison de transmission de couple de rotation étant configurée sous la forme d'une liaison par cannelures ou par arbres dentés.
PCT/DE2016/200083 2015-04-15 2016-02-09 Déphaseur d'arbre à cames comprenant un élément de précontrainte axial WO2016165699A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015206700.9 2015-04-15
DE102015206700.9A DE102015206700A1 (de) 2015-04-15 2015-04-15 Nockenwellenversteller mit einem axialen Vorspannelement

Publications (1)

Publication Number Publication Date
WO2016165699A1 true WO2016165699A1 (fr) 2016-10-20

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PCT/DE2016/200083 WO2016165699A1 (fr) 2015-04-15 2016-02-09 Déphaseur d'arbre à cames comprenant un élément de précontrainte axial

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DE (1) DE102015206700A1 (fr)
WO (1) WO2016165699A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111558824A (zh) * 2019-02-13 2020-08-21 舍弗勒技术股份两合公司 凸轮轴装配方法及配属的凸轮轴调节系统
CN113874605A (zh) * 2019-06-05 2021-12-31 舍弗勒技术股份两合公司 具有油通道的凸轮轴，具有凸轮轴的凸轮轴调整器以及用于凸轮轴调整器的安装方法

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