EP1387047B1 - Moteur à palettes pour dispositif déphaseur d'arbre à cames - Google Patents

Moteur à palettes pour dispositif déphaseur d'arbre à cames Download PDF

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Publication number
EP1387047B1
EP1387047B1 EP03014026A EP03014026A EP1387047B1 EP 1387047 B1 EP1387047 B1 EP 1387047B1 EP 03014026 A EP03014026 A EP 03014026A EP 03014026 A EP03014026 A EP 03014026A EP 1387047 B1 EP1387047 B1 EP 1387047B1
Authority
EP
European Patent Office
Prior art keywords
rotor
stator
vanes
region
oscillating motor
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.)
Expired - Lifetime
Application number
EP03014026A
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German (de)
English (en)
Other versions
EP1387047A3 (fr
EP1387047A2 (fr
Inventor
Ralf Naumann
Gerold Sulka
Frank Heidl
Andreas Knecht
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.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Publication of EP1387047A2 publication Critical patent/EP1387047A2/fr
Publication of EP1387047A3 publication Critical patent/EP1387047A3/fr
Application granted granted Critical
Publication of EP1387047B1 publication Critical patent/EP1387047B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil

Definitions

  • the invention relates to a swivel motor for a camshaft adjusting device according to the preamble of claim 1.
  • Swivel motors for camshaft adjusting devices have a stator and a rotor, which are arranged coaxially with each other and each have wings.
  • the rotor blades abut with their end face on the stator inner wall and can be moved between two adjacent stator blades, which abut sealingly with their end faces on a main body of the rotor.
  • the rotor blades divide the pressure space between two stator blades into two pressure chambers. Depending on the admission of the pressure medium in one of the pressure chambers, the rotor is rotated relative to the stator.
  • the rotor is non-rotatably mounted on the camshaft, which is adjusted in this manner relative to the crankshaft in order to adjust the opening duration of the gas exchange valves of an internal combustion engine to the power to be delivered by the engine.
  • the rotor is non-rotatably mounted on the camshaft, which is adjusted in this manner relative to the crankshaft in order to adjust the opening duration of the gas exchange valves of an internal combustion engine to the power to be delivered by the engine.
  • the US 2002/0029651 A1 already relates to a swivel motor for a camshaft adjusting.
  • a projection is provided at the transition from the side surfaces of a radially inner narrow region in the radially outwardly divergently linear side surfaces of the widened region, so that the areas next to the projection are inevitably recessed relative to the projection.
  • the stator vanes have at the free end on the side surfaces in each case a depression, so that remain in a stop position between the rotor blades and the stator vanes in the region of the body free spaces can get into the pressure medium to rotate the rotor relative to the stator can. In the stop position, the projection partially engages in this free space.
  • From the JP 10 238 319 A is another pivoting motor for a camshaft adjusting known.
  • the side surfaces of the rotor are designed to diverge radially outwardly to increase the length of the sealing gap. Thus, a widened area forms radially outward.
  • the stator vanes have radially outward on the side surfaces in each case a depression, which are provided to achieve a damping effect.
  • the invention has the object of providing the generic pivot motor in such a way that the leakage losses are kept at least low and the swing motor over its service life allows proper adjustment of the camshaft.
  • the inventive rotor motor is achieved by a special design of the rotor blades, that the gap length between the end face of the rotor blades and the stator inner wall is increased without thereby the pivot angle of the rotor is impaired relative to the stator for a given size of the inventive pivot motor. Due to the large width of the radially outer region of the rotor blades, the gap length between the end face of the rotor blade and the stator inner wall is increased, whereby the seal between the two pressure chambers is optimized.
  • the inventive pivot motor therefore has only a slight leakage at most, so that the functional limits of the camshaft adjusting be extended.
  • the pivot angle of the rotor relative to the stator is not reduced for a given size, since the broadening of the rotor blades is discontinuous.
  • the radially inner region of the rotor blades can therefore be kept narrow, so that the pivoting angle of the rotor is not reduced.
  • the swivel motor is used in a camshaft adjusting device, which is used in motor vehicles for the targeted adjustment of the opening duration of gas exchange valves of the internal combustion engine.
  • camshaft adjusting devices and associated swivel motors are known and are therefore not explained in detail.
  • the swivel motor according to the prior art ( FIG. 10 ) has a stator 1 having a cylindrical housing 2 which is closed at one end by a bottom 3 and at the other end by an attached lid (not shown).
  • the stator 1 is drivingly connected to a sprocket 4, via which a chain (not shown) of the camshaft adjusting device is guided.
  • a sprocket 4 On the cylindrical inner wall 5 of the housing 2 are radially inwardly from wings 6, which are arranged uniformly distributed over the circumference and each formed the same.
  • the wings 6 are formed integrally with the housing 2. Between adjacent wings 6 pressure chambers 7 are formed in the pressure medium, preferably hydraulic oil is introduced.
  • the housing bottom 3 and the (not shown) end cover have a central opening through which a camshaft (not shown) projects, rotatably on a rotor 8 is seated.
  • He has a cylindrical body 9, protrude from the radially outward wing 10. They are advantageously integrally formed with the base body 9 and have the same shape.
  • the wings 10 lie with their end faces 11 flat against the inner wall 5 of the stator housing 2.
  • the stator vanes 6 lie with their end faces 12 flat against the cylindrical lateral surface 13 of the main body 9.
  • the pressure chambers 7 are divided into two pressure chambers 14 and 15.
  • the rotor blades 10 abut the stator blades 6.
  • the pressure medium in the pressure chambers 15 is under pressure.
  • the medium contained in the pressure chambers 14 is displaced towards the tank during rotation of the rotor 8 relative to the stator 1 in a known manner. If the rotor 8 is to be rotated in the counterclockwise direction, the pressure chambers 15 are relieved and the pressure medium located in the pressure chambers 14 is pressurized. At least one corresponding valve is provided for this switching.
  • the pressure chambers 15 must be reliably sealed against each other so that the rotor 8 reliably comes into abutment in its respective end position on the side walls of the stator vanes 6 and that the rotor can reliably approach and hold any intermediate position.
  • the end faces 11 of the rotor blades 10 are relatively short in the direction of rotation, so that the leakage over the sealing gap 16 between the inner wall 5 of the stator housing 2 and the end faces 11 of the rotor blades 10 is relatively high.
  • this gap length 16 is increased without the pivoting or rotation angle of the rotor 8 relative to the stator 8 to achieve without structural enlargement of the pivot motor, the rotor blades 10 are widened in their radially outer region ( Fig. 1 and 2 ).
  • this widened region 17 extends approximately over half the radial length of the rotor vanes 10.
  • the radially inner region 18 of the rotor blade adjoining the base body 9 is substantially narrower in comparison to the radially outer, widened region 17.
  • the width of the region 17 in the region of the end face 11 is approximately one and a half to three times the width of the radially inner region 18.
  • the widened wing region 17 is bounded by two flat, radially outwardly diverging side walls 19 and 20, which are continuously curved by the extending end face 11 are interconnected.
  • the two side surfaces 21, 22 extend in the radial direction and parallel to each other and go at an obtuse angle in the side walls 19, 20 over.
  • the stator vanes 6 are adapted to the shape of the rotor blades 10.
  • the stator vanes 6 have side walls 23, 24 adjoining the inner wall 5 of the stator housing 2 at an acute angle, against which the rotor vanes 10 rest in the respective end position with the side walls 19, 20 of their widened portion 17 ( Fig. 1 ). Accordingly, the side walls 23, 24 of the stator vanes 6 diverge radially inwardly.
  • the side walls 23, 24 are flat and go at an obtuse angle in planar side walls 25, 26 on which the rotor blades 10 abut with their side surfaces 21, 22 in the respective end position flat.
  • a groove-shaped recess 27, 28 is provided in each case, which serves as a dirt pocket, are displaced in the befindliches during operation of the pivot motor in the hydraulic medium dirt particles.
  • the rotor 8 can be rotated relative to the stator 1 by a comparatively large angle, without the external dimensions of the stator 1 having to be increased. Nevertheless, the sealing gap 16, which is formed between the end face 11 of the rotor blade 10 and the inner wall 5 of the stator housing 2, due to the widened region 17 has a large length. As a result, the leakage of the swing motor is significantly reduced, since due to the large gap length, the two pressure chambers 14, 15 are sealed on both sides of the rotor blades 8 more effective.
  • Fig. 1 As can be seen, the rotor blades 8 protrude with the transition region 31, 32 (FIG. Fig. 2 ) contributes in the respective stop position partially in the recesses 27, 28 in the region of the housing inner wall 5. This contributes to the fact that the rotor 8 despite broadening its radially outer portion 17 by a relatively large tilt angle the stator 1 can be relatively rotated.
  • the rotor blades 10 are also widened in the circumferential direction in the radially outer region 17, while the radially inner region 18, which adjoins the base body 9, is made relatively narrow.
  • the planar side walls 21, 22 of the inner portion 18 are continuously curved in the planar side walls 19, 20 of the radially outer portion 17 of the rotor blades 10 over.
  • the radially outer, circumferentially widened region 17 of the rotor blades 10 has a smaller radial width than in the previous embodiment. Due to this configuration, the widened portion 17 may be formed even longer in the circumferential direction than in the embodiment according to the Fig.
  • stator 1 to 3 The lying between the housing inner wall 5 and the side walls 23, 24 of the stator 6 recesses 27, 28 are accordingly formed deeper in the circumferential direction than in the previous embodiment. This ensures that the rotor 8 despite the wider end portions 17 of its rotor blades 10 has the same pivot angle as the rotor 8 according to the Fig. 1 to 3 , The outer dimensions of the stator 1 are the same as in the previous embodiment.
  • stator 1 and the rotor 8 are otherwise the same design as in the embodiment of the Fig. 1 to 3 ,
  • the Fig. 7 to 9 show the embodiment of the invention, in which the radially inner portion 18 of the rotor blades 10, which adjoins the cylindrical base body 9 of the rotor 8, two approximately radially extending planar side walls 21, 22 which are shorter in the radial direction than in the two previous embodiments.
  • the radially outer portion 17 of the Rötorhoffl 10 is according to the embodiment of the Fig. 1 to 3 formed and has the planar, radially outwardly diverging side surfaces 19, 20. These side surfaces 19, 20 each pass over a circumferentially extending shoulder 33, 34 in the side walls 21, 22 of the radially inner portion 18 via.
  • the stator vanes 6 have the plane of the housing inner wall radially inwardly diverging planar side surfaces 23, 24, in which the rotor blades 10 in Stop position with their side walls 19, 20 abut surface.
  • the side walls 23, 24 close at an obtuse angle to side walls 35, 36, which are flat and parallel to each other.
  • the rotor blades 10 are in the respective end position with a flat bottom 37, 38 of recesses 39, 40 on the surface, which are provided in the side walls of the rotor blades 10.
  • the bottoms 37, 38 connect approximately at right angles to the shoulders 33, 34, which connect the bottoms 37, 38 with the side surfaces 21, 22.
  • the lateral depressions 39, 40 are provided approximately at half the radial length of the rotor blades 10.
  • the rotor blades 10 protrude with the corner region of their outer, widened regions 17 into the pocket-like recesses 27 and 28, which are provided at the foot of the stator vanes 6.
  • the medium which is located in the direction of rotation in front of the rotor blades 10 pressure chamber, displaced to the tank, while the pressure medium in those chambers, which is located in the direction of rotation behind the rotor blades 10, under pressure is set. Due to the recesses 27, 28 at the foot of the stator 6 and the recesses 29, 30 at the free end of the stator a damping effect is achieved, so that the rotor blades 10 do not hit strongly against the side walls of the stator vanes 6. In the described embodiments, the rotor 8 can rotate relative to the stator 1 by a large angle, since the rotor blades 10 are narrow at the radially inner part 18.
  • the camshaft can be adjusted with respect to the crankshaft with this swivel motor over a large angular range.
  • the leakage of the swing motor is reduced to a considerable extent, as a result of the widened ends 17 of the rotor blade 10 of the sealing gap 16 between the end face 11 of the rotor blade 10 and the housing inner wall 5 is long.
  • the functional limits of the pivoting motor and thus also of the camshaft adjusting device are characterized in comparison with the conventional systems ( Fig. 10 ) significantly expanded.
  • the rotor blades 10 do not widen radially outward steadily, but only in the outer region 17.

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

Claims (9)

  1. Moteur oscillant pour un dispositif déphaseur d'arbre à cames, avec un stator (1) et un rotor (8) pouvant tourner l'un par rapport à l'autre et comportant des ailettes (6, 10) s'étendant dans le plan radial, les ailettes (10) du rotor (8) reposant contre une cloison intérieure du stator (1) et les ailettes (6) du stator (1) reposant avec leurs côtés avant (12) contre une enveloppe d'un corps de base (9) du rotor (8), un renfoncement (39, 40) étant prévu au niveau du rotor (8), dans la zone de transition s'étendant des surfaces latérales (21, 22) d'une zone (18) étroite intérieure dans le plan radial aux surfaces latérales (19, 20), réalisées de façon divergente dans le plan radial vers l'extérieur par rapport à l'accroissement de la longueur du grand espace (16) de la zone élargie (17), les ailettes de stator (6) comportant, au niveau de l'extrémité libre située au niveau des surfaces latérales (23 à 26), respectivement un renfoncement (29, 30), de sorte qu'il reste des espaces libres dans la zone du corps de base (9), entre les ailettes de rotor (10) et les ailettes de stator (6), dans une position de butée, dans lesquels l'agent de pression peut déboucher, pour faire tourner le rotor (8) par rapport au stator (1) ;
    caractérisé en ce que :
    les renfoncements (29, 30) sont prévus en outre pour produire un effet d'amortissement, les ailettes de rotor (10) se rétrécissant en continu uniquement dans la zone (17) élargie extérieure, depuis leur côté avant (11) en direction du corps de base (9) du rotor (8) ;
    les ailettes de rotor (10) reposant à plat, en partant des renfoncements (39, 40), contre les cloisons latérales (35, 36) des ailettes de stator (6), dans la position d'extrémité respective dotée d'un fond (37, 38) plan, ces renfoncements étant prévus dans les cloisons latérales des ailettes (10).
  2. Moteur oscillant selon la revendication 1, caractérisé en ce que la zone (17) élargie des ailettes de rotor (10) se rétrécit dans le plan radial vers l'intérieur en partant du côté avant (11).
  3. Moteur oscillant selon la revendication 1 ou 2, caractérisé en ce que la zone (17) élargie s'étend sur au moins un tiers de la longueur radiale de l'ailette de rotor (10).
  4. Moteur oscillant selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la zone (17) élargie présente, en partant du côté avant (11) de l'ailette de rotor (10), des surfaces latérales (19, 20) convergeant l'une vers l'autre.
  5. Moteur oscillant selon l'une quelconque des revendications 1 à 4, caractérisé en ce que les surfaces latérales (21, 22) de la zone (18) intérieure dans le plan radial s'étendent quasi parallèlement l'une par rapport à l'autre.
  6. Moteur oscillant selon l'une quelconque des revendications 1 à 5, caractérisé en ce que la zone (17) élargie présente, au niveau de son côté avant (11), une largeur correspondant à une fois et demie à trois fois la largeur de la zone (18) intérieure dans le plan radial.
  7. Moteur oscillant selon l'une quelconque des revendications 1 à 6, caractérisé en ce qu'un renfoncement (27, 28) est prévu au niveau de la zone de transition s'étendant des surfaces latérales (23 à 26) des ailettes de stator (6) à la cloison intérieure (5) du stator (1).
  8. Moteur oscillant selon la revendication 7, caractérisé en ce que les ailettes de rotor (10) s'emboîtent dans le renfoncement (27, 28) avec la section (17) élargie, dans la position de butée contre les ailettes de stator (6).
  9. Moteur oscillant selon l'une quelconque des revendications 1 à 8, caractérisé en ce que la zone (18) intérieure dans le plan radial des ailettes (10) a une largeur quasi constante sur l'ensemble de sa longueur.
EP03014026A 2002-07-31 2003-06-23 Moteur à palettes pour dispositif déphaseur d'arbre à cames Expired - Lifetime EP1387047B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10234867A DE10234867A1 (de) 2002-07-31 2002-07-31 Schwenkmotor für eine Nockenwellenverstelleinrichtung
DE10234867 2002-07-31

Publications (3)

Publication Number Publication Date
EP1387047A2 EP1387047A2 (fr) 2004-02-04
EP1387047A3 EP1387047A3 (fr) 2005-07-06
EP1387047B1 true EP1387047B1 (fr) 2011-09-28

Family

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EP03014026A Expired - Lifetime EP1387047B1 (fr) 2002-07-31 2003-06-23 Moteur à palettes pour dispositif déphaseur d'arbre à cames

Country Status (4)

Country Link
US (1) US7275476B2 (fr)
EP (1) EP1387047B1 (fr)
AT (1) ATE526491T1 (fr)
DE (1) DE10234867A1 (fr)

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DE102005007942B4 (de) * 2004-02-27 2007-10-04 Hydraulik-Ring Gmbh Nockenwellenverstelleinrichtung für Brennkraftmaschinen von Kraftfahrzeugen
EP1568855B1 (fr) * 2004-02-27 2007-03-07 Hydraulik-Ring Gmbh Déphaseur d'arbre à cames pour moteur de véhicule
JP5029730B2 (ja) * 2010-06-16 2012-09-19 トヨタ自動車株式会社 可変機構の制御装置
DE102012222271A1 (de) 2012-12-05 2014-06-05 Schaeffler Technologies Gmbh & Co. Kg Hydraulischer Nockenwellenversteller mit einem einen spannungsoptimierten Flügel aufweisenden Rotor
DE102013206078A1 (de) 2013-04-05 2014-10-09 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller
DE102014002362A1 (de) * 2014-02-18 2015-08-20 Daimler Ag Nockenwellenversteller mit einer Anschlagdämpfung
US9341089B2 (en) 2014-04-04 2016-05-17 RB Distribution, Inc. Camshaft phaser
US9957831B2 (en) * 2014-07-31 2018-05-01 The Boeing Company Systems, methods, and apparatus for rotary vane actuators
CN112901302B (zh) * 2019-11-19 2024-04-12 舍弗勒投资(中国)有限公司 凸轮相位调节器

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Also Published As

Publication number Publication date
US20040177751A1 (en) 2004-09-16
ATE526491T1 (de) 2011-10-15
EP1387047A3 (fr) 2005-07-06
EP1387047A2 (fr) 2004-02-04
DE10234867A1 (de) 2004-02-12
US7275476B2 (en) 2007-10-02

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