EP1544420B1 - Internal combustion engine with hydraulic camshaft phasing device - Google Patents
Internal combustion engine with hydraulic camshaft phasing device Download PDFInfo
- Publication number
- EP1544420B1 EP1544420B1 EP04026407A EP04026407A EP1544420B1 EP 1544420 B1 EP1544420 B1 EP 1544420B1 EP 04026407 A EP04026407 A EP 04026407A EP 04026407 A EP04026407 A EP 04026407A EP 1544420 B1 EP1544420 B1 EP 1544420B1
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- European Patent Office
- Prior art keywords
- stator
- walls
- web walls
- web
- rotor
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- 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.)
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Classifications
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- 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
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- 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
- F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
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- 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
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- 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
Definitions
- the invention relates to an internal combustion engine having a hydraulic device for adjusting the rotational angle of a camshaft relative to a crankshaft, comprising: a rotor with vanes disposed thereon, which is non-rotatably connected to the camshaft, a frontally provided with an end wall stator, the rotationally fixed with a driven by the crankshaft Drive wheel is connected, wherein on both sides of the wing pressure chambers are provided which are each bounded by web walls and inner and outer, in the circumferential direction, concentrically extending walls of the stator and are pressurizable or emptied via a hydraulic system with hydraulic fluid.
- From the DE 101 34 320 A1 is an internal combustion engine with a generic Hydraulic device for adjusting the rotational angle of a camshaft known that can change the phase angle of a camshaft relative to a crankshaft.
- This device consists of a rotor and a stator, of which the former, designed as an impeller, comprises the camshaft and rotates synchronously with it.
- the stator is on the one hand closed by a front wall, which may be part of a housing surrounding the stator, and on the other hand by a drive wheel pressure-sealed. It includes the rotor and rotates synchronously with the driven by the crankshaft drive wheel.
- Essentially radially extending web walls in the stator allow only a limited angle of rotation of the rotor and form with this a plurality of pressure chambers, which can be pressurized with hydraulic fluid or emptied.
- a proposal for reducing the weight of the device for adjusting the rotational angle for example, the DE 101 48 687 A1 or the DE 101 34 320 A1 can be removed by parts of the device made of aluminum or an aluminum alloy or another light metal.
- This has the disadvantage that due to different coefficients of thermal expansion, the leakage gaps can increase over the heating and thus results in a high leakage.
- aluminum deforms more under load than steel or iron.
- housing screws together correspondingly large gaps must allow deformation.
- the housing screws represent an increased construction cost, thus causing higher costs and also have a non-optimal power flow for the device result.
- the invention is therefore based on the object to design a device for adjusting the rotational angle of a camshaft relative to a crankshaft for an internal combustion engine such that on the one hand, a reduction in mass of the device takes place on the other hand while minimizing the leakage.
- the DE 199 51 390 A1 discloses a device for hydraulic rotation angle adjustment of a shaft relative to a drive wheel, wherein a wave side arranged plate cooperates with the drive wheel or a drive wheel side arranged component for adjusting the rotational angle.
- the device has at least one ring-shaped formation in the plate and provided on the drive wheel or the component means which cooperate with the formation in such a way that it is subdivided into two separate chambers.
- the device is provided with means for selective hydraulic loading of the chambers for adjusting the relative rotational position of the drive wheel and shaft.
- the object is achieved in a device for an internal combustion engine with the features of the preamble of claim 1, characterized in that essential parts of the stator, in particular its web walls and its inner and outer walls, and optionally the housing with a possibly disposed therein sealing disc produced as chipless Sheet metal parts are formed.
- essential parts of the stator in particular its web walls and its inner and outer walls, and optionally the housing with a possibly disposed therein sealing disc produced as chipless Sheet metal parts are formed.
- sheet instead of sheet also band can be used, being used in the following sheet as a generic term for sheet or strip.
- the solid sintered components as pressure chamber forming units of the drive side are thus replaced by thin-walled sheet metal and Blechumformmaschine.
- these sheets can be ideally adapted to the load locally along the load directions by means of formations or corresponding profilings, without the need for globally larger wall thicknesses and thus a high mass being taken into account .
- this has the advantage that the thermal expansion coefficient of all components remains the same and thus no leaks due to thermal effects can arise.
- the stator consists of inner and outer circumferential walls and web walls.
- the web walls each connect two ends of adjacent inner and outer circumferentially extending walls and extend substantially radially.
- the web walls are not exactly radial, but have a certain angle to the radial or they are not flat, but recesses, for example, to prevent jamming of the wings in their end positions.
- the stator is made of thin-walled sheet metal, it is not as dimensionally stable as a sintered stator known in the art. It is possible to attach the stator directly to the torque-transmitting component via integral connection possibilities. In order to achieve a comparable bending and compression stiffness as that of the sintered stator, but it can be used in a comprehensive housing him ( FIG. 2a ), with the joining technologies of the forming technology or by general force, form, friction-locking technologies such as knurling, flanging, welding, caulking, riveting, gluing or bent retaining lugs is connected to the drive wheel. The housing then takes over the connection of the stator to the drive wheel as torque-transmitting and radial load-transferable component and the seal. It also prevents vibrations from occurring on the stator due to introduced radial forces.
- the housing seals the stator on one end face and forms an end wall there. If the stator walls do not form a right angle to the end wall, the sealing of the pressure chambers is not completely guaranteed. To avoid leakage losses, it is therefore advantageous to arrange a sealing disc immediately in front of the end wall, so that after connecting the end wall with the stator and inserting the rotor with wings perpendicular pressure chambers arise.
- the stability of the housing can be additionally increased by connecting the sealing disc firmly to the end wall.
- the sealing disc is preferably profiled from thin-walled sheet metal and adapted to the size and shape of the stator.
- non-cutting parts made of metal strips. If necessary, as in the case of the stator, the strip must be formed into a ring at one point and then firmly connected, for example by welding.
- the non-cutting production of the stator and the housing of course does not mean that these parts are not machined, if very high accuracy should be required.
- a second way to increase the bending and compressive rigidity of the stator is to form the web walls so that they can transmit radial forces and / or circumferential forces ( FIG. 3a ).
- the support of the radial chain or belt force can internally between stator and rotor or externally between Camshaft or an extension of the rotor and sprocket or made a combination of both possibilities. It has proved particularly advantageous not to form the web walls exactly radially, but make in a range of 10 ° to 30 ° to the radial, so that the wings touch the radially outer web wall ends in their end positions.
- a third embodiment is a tubular stator, the web walls are formed as retracted webs.
- the remaining, closed ring surface saves the housing. This further reduces the mass.
- the sealing washer can be inserted and then sealed the edge and firmly connected.
- the annular surface absorbs the radial forces and prevents the stator from vibrating.
- the radially extending walls may also be formed as open ends, then being used for storage and sealing in the rotor sliding shoes.
- the sliding blocks are designed and arranged such that they support the web walls formed as retracted webs against each other. This prevents bending of the web walls.
- the wall thickness of the radially extending walls of the stator can be further reduced by preventing the vanes of the rotor from abutting and exerting pressure in their respective end positions against the radially extending walls of the stator.
- a Verstellwinkelbegrenzung is necessary. This can, for example, via an associated with the rotor element Verstellwinkelbegrenzung that in a corresponding backdrop engages, be realized.
- the inventively designed device is thus easier compared to a device of the prior art, requires less cutting work and thus reduces the manufacturing costs and can also do without a resin impregnation or steam treatment of sealing the now no longer required sintered material.
- a hydraulic device 1 for the rotational angle adjustment of a camshaft 2 with respect to a crankshaft, not shown, which is designed as a hydraulic actuator.
- This device 1 is driven by a drive wheel 3, which is connected for example by a chain, not shown, with the crankshaft.
- the device 1 consists of a fixedly connected to the drive wheel 3 stator 4, which is closed by a front wall 5 and the drive wheel 3 fluid-tight, and a rotatably connected by an axial central screw 21 with the camshaft 2 rotor 6, wherein the rotor is designed as an impeller.
- the stator 4 of the device 1 forms by web walls 7, 7 ', 7 “and by outer 8, 8', 8” and inner 9, 9 ', 9 “, extending in the circumferential direction walls with the rotor 6 and its wings 10 first pressure chambers 11, 11 ', 11 "and second pressure chambers 12, 12', 12", which, filled with hydraulic fluid, produce an angular displacement between rotor 6 and stator 4.
- the rotor 6 and the stator 4 are arranged in a housing 13 which surrounds the The first 11, 11 ', 11 "and second 12, 12', 12" pressure chambers are sealed to the outside by means of an element 16, which adjoins the rotor 6 for adjustment angle limiting, which engages in a corresponding link 17, limiting the adjustment range of the Rotor 6, which reduces the burden of the stator 4.
- a sealing washer 14 is inserted, which is adapted to the diameter of the stator 4.
- FIG. 2 are the web walls 7, 7 ', 7 "not exactly formed radially, but at an angle of about 20 °, so that the wings 10 in their end positions, the radially outer ends of the web walls 7, 7', 7" touch.
- the bending and compressive rigidity of the stator 4 is increased, and it is possible to transmit radial forces and circumferential forces
- FIG. 3 shows a cross section of a second version of a tubular stator 4. It forms by its substantially radially extending web walls 7, 7 ', 7 "and its inner 8, 8', 8" and outer 9, 9 ', 9 “, in Circumferentially extending walls with the rotor 6, not shown in this figure, the first 11, 11 ', 11 "and second 12, 12', 12" pressure chambers ..
- the stator 4 itself is arranged in a cylindrical housing 13 such that the housing 13 and the outer, circumferentially extending walls 9, 9 ', 9 "touch each other, whereby the rigidity of the stator 4 is increased and vibrations due to radial forces are damped.
- the rigidity can be further increased by filling the hollow chambers or incisions 15, 15 ', 15 "formed by the housings 13 and stator 4, for example, with metal foam, so that the wings 10 do not jam in the end positions, it is advantageous to radially extending web walls in two parts, such that they have at least a first, radially extending part 20, to which the wings abut and at least one further part.
- FIGS. 4a and 4b show a cross-section and a perspective view of a third embodiment of a stator 4.
- this third stator 4 is stiffer with respect to a radial force absorption. It is particularly advantageous to set the web walls such that the respective adjacent web walls 7, 7 'and the housing 13 prevent spreading under radial force (self-locking).
- FIGS. 5a and 5b show a cross section and a perspective view
- a particularly advantageous feature of this design is that the housing 13, with the exception of the end wall 5, can be saved by the remaining, closed annular surface, the circular outer wall 18.
- the sealing disc 14 (FIG. FIG. 1 ), which is used on the front side of the stator 4 and whose edge can be crimped, for example. From the circular outer wall 18 arise by punching, for example, the web walls 7, 7 'which are then bent inwards.
- the web walls 7, 7 ', 7 "are well deformable by their open ends FIG. 6b may be formed and then sealed with sliding shoes 19.
- FIG. 6a and 6b show a perspective view of a part of a fifth and sixth stator 4, the variants of the fifth stator 4 represent.
- These stator variants 4 are therefore inserted into a housing 13.
- a similar rigidity as in the devices of the prior art is achieved by the illustrated embodiments of the stator 4.
- the leakage losses are reduced, as can be dispensed with porous sintered components or a complex steam treatment or resin impregnation.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Gasket Seals (AREA)
Abstract
Description
Die Erfindung betrifft eine Brennkraftmaschine mit einer hydraulischen Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle, umfassend: einen Rotor mit daran angeordneten Flügeln, der drehfest mit der Nockenwelle verbunden ist, einen stirnseitig mit einer Stirnwand versehenen Stator, der drehfest mit einem von der Kurbelwelle angetriebenen Antriebsrad verbunden ist, wobei beiderseits der Flügel Druckkammern vorgesehen sind, die jeweils durch Stegwände und innere sowie äußere, in Umfangsrichtung, konzentrisch zueinander verlaufende Wände des Stators begrenzt sind und über ein Hydrauliksystem mit Hydraulikflüssigkeit druckbeaufschlagbar oder entleerbar sind.The invention relates to an internal combustion engine having a hydraulic device for adjusting the rotational angle of a camshaft relative to a crankshaft, comprising: a rotor with vanes disposed thereon, which is non-rotatably connected to the camshaft, a frontally provided with an end wall stator, the rotationally fixed with a driven by the crankshaft Drive wheel is connected, wherein on both sides of the wing pressure chambers are provided which are each bounded by web walls and inner and outer, in the circumferential direction, concentrically extending walls of the stator and are pressurizable or emptied via a hydraulic system with hydraulic fluid.
Aus der
Nachteilig bei dieser bekannten Vorrichtung ist jedoch, dass die Einzelteile der Vorrichtung vorwiegend aus Stahl oder Eisen bestehen, welche durch Sintern oder Zerspanen hergestellt sind. Daraus resultieren
- 1. eine hohe Masse der Vorrichtung zur Drehwinkelverstellung,
- 2. hohe Fertigungskosten durch den Zerspanungsaufwand bei der Fertigung der Sinterbauteile,
- 3. eine unerwünschte, externe Ölleckage durch die porösen Sinterbauteile.
- 1. a high mass of the device for adjusting the rotational angle,
- 2. high production costs due to the machining outlay during the production of the sintered components,
- 3. undesirable external oil leakage through the porous sintered components.
Weil in der Sintermetallurgie dünne Wandstärken, insbesondere im Zusammenhang mit Wandstärkenschwankungen hinsichtlich Dichteverteilung sowie Festigkeit und Steifigkeit problematisch sind und sich weiterhin komplexe Formen mit unterschiedlichen Füllhöhen oftmals nur mit teuren Schiebern im Werkzeug realisieren lassen, sind bisherige Vorrichtungen zur Drehwinkelverstellung meist aus relativ schweren und massiven Bauteilen gefertigt. Bei spanend hergestellten Vorrichtungen liegt die Problematik ähnlich; komplizierte, der Belastung angepasste Formen sind mit hohem Zerspanungsaufwand verbunden.Because thin wall thicknesses, especially in connection with wall thickness variations in density distribution and strength and rigidity are problematic in the sintered metallurgy and can continue to realize complex shapes with different filling heights often only with expensive sliders in the tool, previous devices for adjusting the angle are usually made of relatively heavy and solid components manufactured. In machined devices, the problem is similar; complicated, adapted to the load shapes are associated with high machining costs.
Ein Vorschlag zur Massereduzierung der Vorrichtung zur Drehwinkelverstellung kann beispielsweise der
Der Erfindung liegt deshalb die Aufgabe zugrunde, eine Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle für eine Brennkraftmaschine derart zu konzipieren, dass einerseits eine Massereduzierung der Vorrichtung erfolgt bei andererseits gleichzeitiger Minimierung der Leckage.The invention is therefore based on the object to design a device for adjusting the rotational angle of a camshaft relative to a crankshaft for an internal combustion engine such that on the one hand, a reduction in mass of the device takes place on the other hand while minimizing the leakage.
Die
Erfindungsgemäß wird die Aufgabe bei einer Vorrichtung für eine Brennkraftmaschine mit den Merkmalen des Oberbegriffs von Anspruch 1 dadurch gelöst, dass wesentliche Teile des Stators, insbesondere seine Stegwände und seine inneren sowie äußeren Wände, sowie gegebenenfalls das Gehäuse mit einer eventuell darin angeordneten Dichtscheibe als spanlos hergestellte Blechteile ausgebildet sind. Selbstverständlich kann statt Blech auch Band verwendet werden, wobei im folgenden Blech als Oberbegriff für Blech oder Band verwendet wird.According to the invention the object is achieved in a device for an internal combustion engine with the features of the preamble of
Die massiven Sinterbauteile als Druckkammer bildende Einheiten der Antriebsseite werden somit durch dünnwandige Blech- und Blechumformteile ersetzt. Weil somit weniger Sinterbauteile gefertigt werden müssen, ergibt sich eine Verringerung des Zerspanungsaufwands und eine Verringerung der externen Ölleckage durch den Wegfall der porösen Sinterteile.The solid sintered components as pressure chamber forming units of the drive side are thus replaced by thin-walled sheet metal and Blechumformteile. Thus, because fewer sintered components need to be manufactured, there is a reduction in the machining cost and a reduction in external oil leakage due to the elimination of the porous sintered parts.
Damit die Vorrichtung trotz ihrer geringeren Masse eine hohe Steifigkeit und Belastbarkeit aufweist, können diese Bleche lokal, entlang den Belastungsrichtungen durch Ausformungen oder entsprechende Profilierungen ideal der Belastung angepasst werden, ohne dass global größere Wandstärken erforderlich sind und damit eine hohe Masse in Kauf genommen werden muss. Gegenüber einer Massereduktion durch Verwendung von Leichtmetall wie beispielsweise in
Der Stator besteht aus inneren und äußeren in Umfangsrichtung verlaufenden Wänden und aus Stegwänden. Die Stegwände verbinden jeweils zwei Enden von benachbarten inneren und äußeren in Umfangsrichtung verlaufenden Wänden und verlaufen im wesentlichen radial. Für einige Statorvarianten ist es vorteilhaft, wenn die Stegwände nicht genau radial verlaufen, sondern einen gewissen Winkel zur Radialen aufweisen oder sie nicht eben ausgebildet sind, sondern Vertiefungen aufweisen, um beispielsweise ein Verklemmen der Flügel in ihren Endstellungen zu verhindern.The stator consists of inner and outer circumferential walls and web walls. The web walls each connect two ends of adjacent inner and outer circumferentially extending walls and extend substantially radially. For some Statorvarianten it is advantageous if the web walls are not exactly radial, but have a certain angle to the radial or they are not flat, but recesses, for example, to prevent jamming of the wings in their end positions.
Weil der Stator aus dünnwandigem Blech hergestellt ist, ist er nicht so formstabil wie ein aus dem Stand der Technik bekannter, gesinterter Stator. Es besteht die Möglichkeit, den Stator direkt über stoffschlüssige Verbindungsmöglichkeiten an die momentenübertragende Komponente anzubringen. Um eine vergleichbare Biege- und Drucksteifigkeit wie die des gesinterten Stators zu erzielen, kann er aber in ein ihn umfassendes Gehäuse eingesetzt werden (
Das Gehäuse dichtet den Stator auf einer Stirnseite ab und bildet dort eine Stirnwand. Wenn die Statorwände zur Stirnwand keinen rechtwinkligen Winkel bilden, ist die Abdichtung der Druckkammern nicht vollständig gewährleistet. Um Leckageverluste zu vermeiden, ist es daher vorteilhaft, eine Dichtscheibe unmittelbar vor der Stirnwand anzuordnen, so dass nach Verbinden der Stirnwand mit dem Stator und Einsetzen des Rotors mit Flügeln rechtwinklige Druckkammern entstehen. Die Stabilität des Gehäuses kann zusätzlich erhöht werden, wenn man die Dichtscheibe fest mit der Stirnwand verbindet. Die Dichtscheibe ist vorzugsweise aus dünnwandigem Blech profiliert und an Größe und Form des Stators angepasst.The housing seals the stator on one end face and forms an end wall there. If the stator walls do not form a right angle to the end wall, the sealing of the pressure chambers is not completely guaranteed. To avoid leakage losses, it is therefore advantageous to arrange a sealing disc immediately in front of the end wall, so that after connecting the end wall with the stator and inserting the rotor with wings perpendicular pressure chambers arise. The stability of the housing can be additionally increased by connecting the sealing disc firmly to the end wall. The sealing disc is preferably profiled from thin-walled sheet metal and adapted to the size and shape of the stator.
Der Zusammenhalt der Teile Stator, Gehäuse und Dichtscheibe wird durch oben angeführte Verbindungstechnologien der Umformtechnik gewährleistet. Gegenüber der axialen, kraftschlüssigen Schraubverbindung werden Druckspannungsverformungen reduziert; außerdem wird vorteilhafterweise kein zusätzliches Bauteil benötigt und der Montageaufwand vermindert.The cohesion of the parts stator, housing and sealing disc is ensured by the above-mentioned joining technologies of forming technology. Compared with the axial, non-positive screw connection, compressive stress deformations are reduced; In addition, advantageously no additional component is needed and reduces assembly costs.
Es ist zweckmäßig, die spanlos hergestellten Teile aus Blechstreifen zu formen. Gegebenenfalls muss - wie beim Stator - an einer Stelle der Streifen zu einem Ring geformt und dann fest verbunden werden, beispielsweise durch Verschweißen. Die spanlose Herstellung des Stators und des Gehäuses bedeutet selbstverständlich nicht, dass diese Teile nicht spanend nachbearbeitet werden, sofern eine sehr hohe Genauigkeit erforderlich sein sollte.It is expedient to form the non-cutting parts made of metal strips. If necessary, as in the case of the stator, the strip must be formed into a ring at one point and then firmly connected, for example by welding. The non-cutting production of the stator and the housing of course does not mean that these parts are not machined, if very high accuracy should be required.
Eine zweite Möglichkeit, um die Biege und Drucksteifigkeit des Stators zu erhöhen, ist es, die Stegwände so auszubilden, dass sie Radialkräfte und/oder Umfangskräfte übertragen können (
Eine dritte Ausbildung ist ein rohrförmiger Stator, dessen Stegwände als eingezogene Stege ausgebildet sind. Durch die verbleibende, geschlossene Ringfläche wird das Gehäuse eingespart. Dadurch wird die Masse weiter verringert. Zwischen Rand und den radial verlaufenden Wänden kann die Dichtscheibe eingelegt und dann der Rand abgedichtet und fest verbunden werden. Bei dieser Ausführung nimmt die Ringfläche die Radialkräfte auf und verhindert ein Schwingen des Stators.A third embodiment is a tubular stator, the web walls are formed as retracted webs. The remaining, closed ring surface saves the housing. This further reduces the mass. Between the edge and the radially extending walls, the sealing washer can be inserted and then sealed the edge and firmly connected. In this embodiment, the annular surface absorbs the radial forces and prevents the stator from vibrating.
Um eine bessere Umformbarkeit zu erreichen, können die radial verlaufenden Wände auch als offene Enden ausgebildet sein, wobei dann zur Lagerung und Abdichtung im Rotor Gleitschuhe verwendet werden. Die Gleitschuhe sind derart ausgebildet und angeordnet, dass sie die als eingezogene Stege ausgebildeten Stegwände gegeneinander abstützen. Sie verhindern damit ein Verbiegen der Stegwände.In order to achieve a better formability, the radially extending walls may also be formed as open ends, then being used for storage and sealing in the rotor sliding shoes. The sliding blocks are designed and arranged such that they support the web walls formed as retracted webs against each other. This prevents bending of the web walls.
Die zwischen den Stegwänden sich befindenden Räume, entweder Hohlräume oder Einschnitte, werden mit Kunststoff um- oder ausgespritzt oder Metall geschäumt. Dadurch wird das Profil der im wesentlichen radial verlaufenden Stegwände versteift und eine hohe Dichtheit der Druckkammern untereinander sowie nach außen sicher gestellt.The spaces located between the web walls, either cavities or cuts, are plastic-injected or sprayed or metal foamed. As a result, the profile of the substantially radially extending web walls is stiffened and a high tightness of the pressure chambers with each other and made safe to the outside.
Die Wandstärke der radial verlaufenden Wände des Stators kann weiter reduziert werden, wenn verhindert wird, dass die Flügel des Rotors in ihren jeweiligen Endpositionen an die radial verlaufenden Wände des Stators anschlagen und Druck auf diese ausüben. Dazu ist eine Verstellwinkelbegrenzung notwendig. Diese kann beispielsweise über ein mit dem Rotor in Verbindung stehendes Element zur Verstellwinkelbegrenzung, das in eine korrespondierende Kulisse eingreift, realisiert werden.The wall thickness of the radially extending walls of the stator can be further reduced by preventing the vanes of the rotor from abutting and exerting pressure in their respective end positions against the radially extending walls of the stator. For this purpose, a Verstellwinkelbegrenzung is necessary. This can, for example, via an associated with the rotor element Verstellwinkelbegrenzung that in a corresponding backdrop engages, be realized.
Die erfindungsgemäß ausgebildete Vorrichtung ist also gegenüber einer Vorrichtung des Standes der Technik leichter, benötigt weniger Zerspanungsaufwand und reduziert damit die Fertigungskosten und kann auch auf eine Kunstharzimprägnierung oder Wasserdampfbehandlung des zur Abdichtung des nun nicht mehr benötigten Sinterwerkstoffs verzichten.The inventively designed device is thus easier compared to a device of the prior art, requires less cutting work and thus reduces the manufacturing costs and can also do without a resin impregnation or steam treatment of sealing the now no longer required sintered material.
Die Erfindung wird nachfolgend anhand von Ausführungsbeispielen näher erläutert und in den dazu gehörigen Zeichnungen schematisch dargestellt.
Es zeigen
Figur 1- einen Längsschnitt einer Vorrichtung zur Drehwinkelverstellung, wobei ein spanlos ausgebildeter Stator in einem Außengehäuse eingesetzt ist;
Figur 2- einen Querschnitt durch eine Vorrichtung zur Drehwinkelverstellung,
- Figur 3
- einen Querschnitt einer zweiten Ausführung eines Stators,
- Figur 4a
- einen Querschnitt einer dritten Ausführung eines Stators,
- Figur 4b
- eine perspektivische Ansicht des Stators gemäß
Figur 4a , - Figur 5a
- einen Querschnitt einer vierten Ausführung eines Stators, dessen äußere Ringfläche geschlossen ist,
- Figur 5b
- eine perspektivische Ansicht des Stators gemäß
Figur 5a , - Figur 6a
- eine perspektivische Ansicht auf eine äußere, in Umfangsrichtung verlaufende Wand und nach außen ausgeformte Stegwände einer fünften Ausführung eines Stators
- Figur 6b
- eine perspektivische Ansicht auf eine äußere, in Umfangsrichtung verlaufende Wand und nach innen ausgeformte Stegwände einer sechsten Ausführung eines Stators mit einem Gleitschuh.
Show it
- FIG. 1
- a longitudinal section of a device for adjusting the rotational angle, wherein a chipless formed stator is inserted in an outer housing;
- FIG. 2
- a cross section through a device for adjusting the rotational angle,
- FIG. 3
- a cross section of a second embodiment of a stator,
- FIG. 4a
- a cross section of a third embodiment of a stator,
- FIG. 4b
- a perspective view of the stator according to
FIG. 4a . - FIG. 5a
- a cross section of a fourth embodiment of a stator whose outer annular surface is closed,
- FIG. 5b
- a perspective view of the stator according to
FIG. 5a . - FIG. 6a
- a perspective view of an outer, circumferentially extending wall and outwardly shaped web walls of a fifth embodiment of a stator
- FIG. 6b
- a perspective view of an outer, circumferentially extending wall and inwardly molded web walls of a sixth embodiment of a stator with a sliding block.
Aus den
Zwecks Abdichtung der Druckkammern 11, 11', 11", 12, 12', 12" ist zwischen Gehäuse 13 und Stator 4 eine Dichtscheibe 14 eingelegt, welche dem Durchmesser des Stators 4 angepasst ist.For the purpose of sealing the
In
Die
Die
Die
Zusammenfassend ergibt sich durch die spanlos hergestellten Bauteile, insbesondere durch wesentliche Teile des Stators 4, eine große Massereduzierung der Vorrichtung. Eine ähnliche Steifigkeit wie bei den Vorrichtungen des Standes der Technik wird durch die dargestellten Ausführungsformen des Stators 4 erreicht. Gleichzeitig werden die Leckageverluste gemindert, da auf poröse Sinterbauteile bzw. auf eine aufwändige Wasserdampfbehandlung oder Kunstharzimprägnierung verzichtet werden kann.In summary, results from the non-cutting produced components, in particular by essential parts of the
- 11
- hydraulische Vorrichtung zur Drehwinkelverstellunghydraulic device for adjusting the angle of rotation
- 22
- Nockenwellecamshaft
- 33
- Antriebsraddrive wheel
- 44
- Statorstator
- 55
- Stirnwandbulkhead
- 66
- Rotorrotor
- 7, 7', 7"7, 7 ', 7 "
- Stegwändeweb walls
- 8, 8', 8"8, 8 ', 8 "
- äußere, in Umfangsrichtung verlaufende Wändeouter, circumferentially extending walls
- 9,9',9"9,9 ', 9 "
- innere, in Umfangsrichtung verlaufende Wändeinner, circumferentially extending walls
- 1010
- Flügelwing
- 11, 11', 11"11, 11 ', 11 "
- erste Druckkammernfirst pressure chambers
- 12, 12', 12"12, 12 ', 12 "
- zweite Druckkammernsecond pressure chambers
- 1313
- Außengehäuseouter casing
- 1414
- Dichtscheibesealing washer
- 15, 15', 15"15, 15 ', 15 "
- Hohlkammern oder EinschnitteHollow chambers or incisions
- 1616
- Element zur VerstellwinkelbegrenzungElement for adjustment angle limitation
- 1717
- Kulissescenery
- 1818
- kreisrunde Außenwandcircular outer wall
- 1919
- Gleitschuhshoe
- 2020
- erster, radial verlaufender Teil der Stegwandfirst, radially extending part of the web wall
- 2121
- axiale Zentralschraubeaxial central screw
Claims (14)
- Internal combustion engine having a hydraulic device (1) for rotational angle adjustment of a camshaft (2) relative to a crankshaft, comprising: a rotor (6) which has vanes (10) arranged thereon and is rotationally fixedly connected to the camshaft (2), a stator (4) which is provided at at least one end side with an end wall (5) and has substantially a cylindrical outer contour and is rotationally fixedly connected to a drive wheel (3) which is driven by the crankshaft, with pressure chambers (11, 11', 11", 12, 12', 12") being provided at both sides of the vanes (10), which pressure chambers are delimited in each case by web walls (7, 7', 7") and inner (9, 9', 9") and outer (8, 8', 8") walls, which run in the circumferential direction concentrically with respect to one another, of the stator (4) and can be pressurized with hydraulic fluid or emptied by means of a hydraulic system, with the stator (4), including its web walls (7, 7', 7") and its inner and outer walls (8, 8', 8", 9, 9', 9") which run in the circumferential direction, being formed as a strip part or sheet-metal part produced in a non-cutting process, characterized in that the pressure chambers (11, 11', 11", 12, 12', 12") are closed off at the end side by a circular-ringshaped sealing disc (14) which is formed as a sheet-metal part.
- Device according to Claim 1, characterized in that the stator (4) is reinforced locally at particularly loaded points, along the loading directions, by mouldings, beads or corresponding profiles.
- Device according to Claim 1, characterized in that the stator (4) has an outer housing (13) which is preferably tubular and formed as a sheet-metal part and which comprises the web walls (7, 7', 7") and the outer (8, 8', 8") and inner (9, 9', 9") walls in the circumferential direction.
- Device according to Claim 1, characterized in that the stator (4), housing (13) and drive wheel (3) are fastened to one another by connecting techniques from the field of forming technology, for example knurling, flanging, welding, calking, riveting, adhesive bonding or bent holding lugs.
- Device according to Claim 1, characterized in that the sealing disc (14) is fixedly connected to the end wall (5) which is formed in one piece with the outer housing (13).
- Device according to Claim 1, characterized in that an element (16) for adjustment angle limitation is arranged in the rotor (6), which element (16) engages into a corresponding sliding-block guide (17).
- Device according to Claim 1, characterized in that the stator (4) is composed of alternating outer walls (8, 8', 8") which run in the circumferential direction and inner walls (9, 9', 9") which run in the circumferential direction, which walls are in each case sections of a circular cylinder, with in each case adjacent outer (8, 8', 8") and inner (9, 9', 9") walls which run in the circumferential direction being connected by web walls (7, 7', 7") which, together with a circular rotor (6) which is inserted into the stator and the vanes (10) arranged in said rotor (6), form pressure chambers (11, 11', 11", 12, 12', 12"), and at their sides facing away from the pressure chambers, form cavities or indentations (15, 15', 15").
- Device according to Claim 7, characterized in that the cavities or indentations (15, 15', 15") are filled with metal foams or are extrusion coated with plastic or filled with plastic by injection moulding.
- Device according to Claim 7, characterized in that the web walls (7, 7', 7") run or are formed such that, in the end positions, the vanes (10) abut against the web walls (7, 7', 7") either only at their radially outer end, only at their radially inner end or only in a central region.
- Device according to Claim 7, characterized in that the web walls (7, 7', 7") are formed as webs drawn inward or drawn outward in pairs out of the circumferential wall of an outer cylinder or inner cylinder.
- Device according to Claim 10, characterized in that the web walls (7, 7', 7") are punched out of the inner or outer circumferential wall of the stator (3) and are bent outward or inward in the radial direction in pairs.
- Device according to Claim 11, characterized in that the web walls (7, 7', 7") are connected in pairs by a sliding shoe (19) which supports them, and form cavities (15, 15', 15").
- Device according to Claim 12, characterized in that the cavities (15, 15', 15") are filled with metal foams or are extrusion coated with plastic or filled with plastic by injection moulding.
- Device according to Claim 7, characterized in that the web walls (7, 7', 7") form an angle of 10° to 30° with respect to the radial, such that the vanes, in their end positions, make contact only with the radially outer ends of the web walls (7, 7',7").
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10358888.4A DE10358888B4 (en) | 2003-12-16 | 2003-12-16 | Internal combustion engine with a hydraulic device for adjusting the rotational angle of a camshaft relative to a crankshaft |
DE10358888 | 2003-12-16 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1544420A2 EP1544420A2 (en) | 2005-06-22 |
EP1544420A3 EP1544420A3 (en) | 2008-08-27 |
EP1544420B1 true EP1544420B1 (en) | 2010-07-28 |
Family
ID=34485404
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04026407A Not-in-force EP1544420B1 (en) | 2003-12-16 | 2004-11-06 | Internal combustion engine with hydraulic camshaft phasing device |
Country Status (9)
Country | Link |
---|---|
US (1) | US7284516B2 (en) |
EP (1) | EP1544420B1 (en) |
JP (1) | JP4608300B2 (en) |
KR (1) | KR101119457B1 (en) |
CN (1) | CN100439663C (en) |
AT (1) | ATE475783T1 (en) |
BR (1) | BRPI0406256B1 (en) |
DE (2) | DE10358888B4 (en) |
RU (1) | RU2353782C2 (en) |
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DE102004041430A1 (en) | 2004-08-27 | 2006-03-09 | Daimlerchrysler Ag | Phaser |
DE102004062036A1 (en) * | 2004-12-23 | 2006-07-27 | Schaeffler Kg | Camshaft adjuster for an internal combustion engine |
DE102005024242B4 (en) * | 2005-05-23 | 2017-08-24 | Schaeffler Technologies AG & Co. KG | Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine |
DE102005024241B4 (en) * | 2005-05-23 | 2017-08-17 | Schaeffler Technologies AG & Co. KG | Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine |
GB2431977A (en) * | 2005-11-02 | 2007-05-09 | Mechadyne Plc | Camshaft assembly |
DE102006036052B4 (en) * | 2006-08-02 | 2018-03-08 | Schaeffler Technologies AG & Co. KG | Sealing plate for a camshaft adjuster and camshaft adjuster with a sealing plate |
DE102007039282B4 (en) | 2007-08-20 | 2017-06-01 | Hilite Germany Gmbh | Hydraulically sealed camshaft adjuster |
DE102007056550A1 (en) * | 2007-11-23 | 2009-05-28 | Schaeffler Kg | Modular built-up camshaft adjuster with chain or belt pulley |
DE102008032031A1 (en) | 2008-07-07 | 2010-01-14 | Schaeffler Kg | Phaser |
DE102009041768B4 (en) * | 2008-10-09 | 2020-10-08 | Schaeffler Technologies AG & Co. KG | Camshaft adjuster for a concentric camshaft |
JP4900451B2 (en) * | 2009-11-09 | 2012-03-21 | 株式会社デンソー | Valve timing adjustment device |
DE102010022897A1 (en) * | 2010-06-07 | 2011-12-08 | Schaeffler Technologies Gmbh & Co. Kg | Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine and screw for such a device |
DE102010024596A1 (en) * | 2010-06-22 | 2011-12-22 | Schaeffler Technologies Gmbh & Co. Kg | Device for controlling and / or influencing the valve timing of an internal combustion engine |
JP5177715B2 (en) * | 2010-12-02 | 2013-04-10 | 株式会社デンソー | Valve timing adjusting device and assembling method thereof |
DE102010063706A1 (en) | 2010-12-21 | 2012-06-21 | Schaeffler Technologies Gmbh & Co. Kg | Camshaft adjuster with return spring |
JP5569458B2 (en) * | 2011-04-18 | 2014-08-13 | 株式会社デンソー | Valve timing adjustment device |
JP5929300B2 (en) * | 2011-08-08 | 2016-06-01 | 日産自動車株式会社 | Engine valve timing control device |
US9175571B2 (en) * | 2012-03-19 | 2015-11-03 | General Electric Company | Connecting system for metal components and CMC components, a turbine blade retaining system and a rotating component retaining system |
DE102012205705B4 (en) * | 2012-04-05 | 2018-02-08 | Schaeffler Technologies AG & Co. KG | Camshaft adjuster with a front and / or output element in sandwich construction and a method for producing the input or output element in sandwich construction |
DE102012218405B4 (en) * | 2012-10-10 | 2014-08-21 | Schaeffler Technologies Gmbh & Co. Kg | Camshaft adjuster with rolled connection |
CN102926831A (en) * | 2012-10-30 | 2013-02-13 | 芜湖杰锋汽车动力系统有限公司 | Air distribution adjusting device |
DE102013204929A1 (en) * | 2013-03-20 | 2014-09-25 | Schaeffler Technologies Gmbh & Co. Kg | Phaser |
DE102014200818A1 (en) * | 2014-01-17 | 2015-01-08 | Schaeffler Technologies Gmbh & Co. Kg | Two-part stator with cold-welded lid |
CN103953408B (en) * | 2014-04-30 | 2016-08-17 | 桂林电子科技大学 | Electrodeless variable valve timing mechanism |
DE102016220829A1 (en) | 2016-10-24 | 2018-04-26 | Schaeffler Technologies AG & Co. KG | Stator with successively arranged pressure chamber segments and camshaft adjuster |
DE102020119092A1 (en) * | 2019-07-25 | 2021-01-28 | ECO Holding 1 GmbH | Method for producing a camshaft adjuster and a camshaft adjuster |
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DE19546103A1 (en) * | 1995-12-11 | 1997-06-12 | Schaeffler Waelzlager Kg | Device for changing the timing of an internal combustion engine |
CN1223331A (en) * | 1997-12-17 | 1999-07-21 | F·波尔希名誉工学博士公司 | Device for regulating relative position between one axle and driving wheel |
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JP2000045727A (en) * | 1998-08-04 | 2000-02-15 | Mitsubishi Electric Corp | Hydraulic valve timing adjusting device and its assembly method |
JP2000064814A (en) | 1998-08-21 | 2000-02-29 | Mitsubishi Electric Corp | Valve timing varying device for internal combustion engine and manufacture of case therefor |
DE19908934A1 (en) * | 1999-03-02 | 2000-09-07 | Schaeffler Waelzlager Ohg | Device for adjusting the angle of rotation of a camshaft |
JP2000297614A (en) * | 1999-04-12 | 2000-10-24 | Toyota Motor Corp | Valve timing control device for internal combustion engine |
DE19916644A1 (en) * | 1999-04-14 | 2000-10-19 | Schaeffler Waelzlager Ohg | Device for adjusting the angle of rotation of a camshaft relative to the crankshaft of a reciprocating piston internal combustion engine |
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DE19951390A1 (en) | 1999-10-26 | 2001-05-03 | Schaeffler Waelzlager Ohg | Device for the hydraulic rotation angle adjustment of a shaft relative to a drive wheel |
US6247434B1 (en) * | 1999-12-28 | 2001-06-19 | Borgwarner Inc. | Multi-position variable camshaft timing system actuated by engine oil |
DE10029317A1 (en) * | 2000-06-20 | 2002-01-10 | Hasse & Wrede Gmbh | Method for producing a torsional vibration damper housing, in particular a housing for a viscosity torsional vibration damper |
JP2002097911A (en) * | 2000-09-22 | 2002-04-05 | Aisin Seiki Co Ltd | Valve opening and closing timing control device |
JP2002180809A (en) | 2000-10-04 | 2002-06-26 | Denso Corp | Method of manufacturing valve timing adjusting device |
DE10134320A1 (en) | 2001-07-14 | 2003-01-23 | Ina Schaeffler Kg | Device for changing the control times of gas shuttle valves in internal combustion engines comprises a driven unit axially, radially and peripherally locked on a sleeve and screwed in a deformation-free manner on a camshaft |
DE10205415A1 (en) * | 2002-02-09 | 2003-08-28 | Porsche Ag | Device for the relative rotation angle adjustment of a camshaft of an internal combustion engine to a drive wheel |
-
2003
- 2003-12-16 DE DE10358888.4A patent/DE10358888B4/en not_active Expired - Fee Related
-
2004
- 2004-11-06 EP EP04026407A patent/EP1544420B1/en not_active Not-in-force
- 2004-11-06 DE DE502004011438T patent/DE502004011438D1/en active Active
- 2004-11-06 AT AT04026407T patent/ATE475783T1/en not_active IP Right Cessation
- 2004-12-13 JP JP2004360456A patent/JP4608300B2/en not_active Expired - Fee Related
- 2004-12-15 BR BRPI0406256A patent/BRPI0406256B1/en not_active IP Right Cessation
- 2004-12-15 RU RU2004136796/06A patent/RU2353782C2/en not_active IP Right Cessation
- 2004-12-15 US US11/012,883 patent/US7284516B2/en active Active
- 2004-12-16 CN CNB2004101011688A patent/CN100439663C/en not_active Expired - Fee Related
- 2004-12-16 KR KR1020040106808A patent/KR101119457B1/en not_active IP Right Cessation
Also Published As
Publication number | Publication date |
---|---|
US20050155567A1 (en) | 2005-07-21 |
EP1544420A2 (en) | 2005-06-22 |
RU2353782C2 (en) | 2009-04-27 |
KR20050061354A (en) | 2005-06-22 |
BRPI0406256A (en) | 2005-09-06 |
DE502004011438D1 (en) | 2010-09-09 |
EP1544420A3 (en) | 2008-08-27 |
JP2005180434A (en) | 2005-07-07 |
CN1629453A (en) | 2005-06-22 |
US7284516B2 (en) | 2007-10-23 |
ATE475783T1 (en) | 2010-08-15 |
CN100439663C (en) | 2008-12-03 |
KR101119457B1 (en) | 2012-03-15 |
DE10358888A1 (en) | 2005-07-21 |
JP4608300B2 (en) | 2011-01-12 |
DE10358888B4 (en) | 2018-12-27 |
RU2004136796A (en) | 2006-05-27 |
BRPI0406256B1 (en) | 2017-04-04 |
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