EP1753941A1 - Flügelzellen-nockenwellenversteller - Google Patents
Flügelzellen-nockenwellenverstellerInfo
- Publication number
- EP1753941A1 EP1753941A1 EP05739591A EP05739591A EP1753941A1 EP 1753941 A1 EP1753941 A1 EP 1753941A1 EP 05739591 A EP05739591 A EP 05739591A EP 05739591 A EP05739591 A EP 05739591A EP 1753941 A1 EP1753941 A1 EP 1753941A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- section
- groove
- vane
- cross
- camshaft adjuster
- 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.)
- Granted
Links
- 230000007704 transition Effects 0.000 claims description 8
- 239000000463 material Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
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
-
- 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
-
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2101—Cams
- Y10T74/2102—Adjustable
Definitions
- the invention relates to a vane-type camshaft adjuster with a stator and a rotor which can be rotated hydraulically relative to the stator and can be connected to a camshaft and has radially projecting vanes inserted into vane grooves.
- Camshaft adjusters are used to change the timing for opening or closing the valves. This removes the fixed angular relationship between the camshaft and the crankshaft driving it, and the control times can be optimally set depending on the engine speed and other parameters. Camshaft adjusters allow the camshaft to rotate relative to the crankshaft.
- Known vane-cell camshaft adjusters have a rotor with a plurality of radially projecting vanes which are pressed radially outward against a stator housing by the force of a spring.
- a plurality of radially inwardly projecting stops are formed on the stator, which limit the adjustment movement of the rotor in both directions of rotation when the blades run against the stops.
- the wings rest with their end edges on the stator, so that between each wing side and the adjacent side of a stop of the stator, a chamber is formed, into which a fluid, usually the engine oil, is conveyed via a valve assigned to the camshaft adjuster.
- the stator serves on the one hand to separate and seal the fluid chambers, on the other hand to determine the adjustment angle between the camshaft and the crankshaft.
- the rotor of the camshaft adjuster is non-positively connected to the camshaft by means of a screw.
- the rotor (rotary piston) of the adjuster is pressed by the pretensioning force of the central screw with its lateral flange surface against the corresponding side surface of the camshaft.
- the frictional connection must transmit the drive torque and any axial or radial forces from the drive. Therefore, a relatively high preload must be applied.
- it has been found that relatively high tensile stresses are generated in the rotor on the side facing the camshaft in the groove base of the wing grooves.
- the invention is therefore based on the problem of specifying a vane-type camshaft adjuster in which the voltage concentration on the camshaft side is reduced. To solve this problem, it is provided according to the invention in a vane-cell camshaft adjuster of the type mentioned at the outset that the camshaft-side end section of the wing groove has an enlarged cross section.
- the invention is based on the knowledge that the stresses in the area of the groove base of the wing groove, which arise from the pretensioning force of the central screw, are locally limited in the axial direction of the rotor to the area of the flange surface which, when installed, adjoins the camshaft. According to the invention, only this limited area is equipped with a tension-optimized contour, while the remaining area of the wing groove retains the conventional functional contour for optimal guidance of the wing and the wing spring.
- the notch effect is reduced by the enlarged cross section in the area of the cam section on the end section of the wing groove, and there is a more uniform stress distribution over the width with considerably reduced stress peaks.
- a particularly effective reduction of the stress peaks can be achieved if the wing groove is undercut in the area of the groove base with respect to the groove side surfaces and has an enlarged cross section at this point.
- the most vulnerable area, which is located on the undercut is thus relieved by the choice of an enlarged cross section.
- the rest of the area, which is spaced from the contact surface of the rotor soapy with the camshaft, remains unchanged.
- the enlarged area can be located on the one hand in the area of the groove base, but it can also be provided in the area of the undercut, furthermore the area with an enlarged cross section can be provided both in the area of the groove base and in the area of the undercut or in both areas.
- a particularly favorable stress curve results if the transition between the non-enlarged and the enlarged groove cross section is curved. is shaped.
- the transition between the two cross sections with different diameters, which is designed as an arc, causes a gradual increase in stress, so that local stress peaks are avoided.
- the wing groove in the area of the undercut and the groove base has a radially outwardly extending section with an enlarged cross section.
- the area that extends radially outward from the base of the groove is optimized.
- the original groove base and the groove base in the end section can have a common base line.
- the cross section of the enlarged area can be approximately oval and have a straight section in the area of the groove base. It is also possible for the enlarged section to have a constant diameter, at least approximately. Such a structure is particularly inexpensive to manufacture.
- the section of the wing groove merges into a section with a continuously increasing cross section.
- the wing groove can be left unchanged, while from there it widens outward in a radial direction in the manner of a goblet.
- an oval cross section of the enlarged area is preferred.
- the continuous transition between the wing groove with the normal cross-section and the section with the enlarged cross-section avoids increased stress concentrations on the side surface against which the camshaft rests. Accordingly, it is not necessary to use a material with a higher strength and the subject matter of the invention can be manufactured inexpensively.
- the wing groove in the area of the groove basically has a radially inward section with an enlarged cross section.
- This area with the enlarged cross section is preferably present in addition to the section with the enlarged cross section, which is located in the area of the undercut and in the groove base and extends radially outward.
- the entire area surrounding the undercut, the groove base and the beginning of the groove side surfaces can have the enlarged diameter. Since there are no sharp-edged transitions at any point, there are no local voltage peaks.
- the area with the enlarged cross section has an oval basic shape and is conical.
- FIG. 1 shows a cross section through a vane-camshaft adjuster.
- FIG. 2a shows a perspective view of the rotor of a vane-cell camshaft adjuster according to the invention
- Fig. 2b is a side view of the rotor shown in Fig. 1;
- FIG. 1 shows a cross section through a vane-cell camshaft adjuster
- FIG. 2a shows a perspective view of a rotor 1 of a vane-cell camshaft adjuster 0.
- the rotor 1 has a disk-shaped basic shape and has five evenly distributed vane grooves 2, into which vanes 2a can be inserted, which seal oil-fillable chambers 2b between the rotor 1 and a stator 2c. On the left and right side of each wing groove 2 there are bores 3, 4 through which the oil can flow into and out of the mentioned chambers 2b.
- the wing groove 2 extends in the axial direction and has an enlarged cross section at its end section 5.
- FIG. 2 b shows a sectional side view of the rotor 1 shown in FIG. 1. It can be seen particularly well in this illustration that the wing groove 2 has a constant cross section in the axial direction almost over the entire thickness of the rotor 1 and only in the region of the end section 5 has an enlarged cross section. This increase in cross section leads to a reduction in the notch effect and thus to lower stress peaks in the region of the end section 5.
- FIGS. 3a-c are enlarged representations of the end section of the wing groove 9 of a rotor according to the prior art.
- 3a is a perspective view
- FIG. 3b is a side view analogous to FIG. 2
- FIG. 3c is a front view of the wing groove 9.
- the groove side surfaces 6 point in the vicinity of the groove base 8 an undercut 7, which consists of curved sections and straight pieces.
- the wing groove 9 instructs the free end 10 has the same constant diameter as in the rest of the area, so that there is a relatively large cross-sectional jump at this point, which causes the increased stresses.
- Figures 4a-c show a first embodiment of the invention.
- the transition 11 between the non-enlarged and the enlarged groove cross section is designed in an arc shape.
- the transition 11 extends both from the groove base 12 and from the undercuts 13 to the outside.
- the arcuate transition 11 causes a comparatively gentle deflection of force which, in addition to the enlarged cross section on the outside, leads to lower stress concentrations.
- Figures 5a-c show a second embodiment of the invention.
- the wing groove has a section 14 which extends radially outwards, that is to say to the opening of the wing groove, and has an enlarged diameter.
- the diameter of section 14 is constant.
- the area with the enlarged cross section does not extend radially inward from the groove base 12. The desired reduction in tension is achieved in this variant primarily by the enlarged diameter.
- Figures 6a-c show a third embodiment of the invention.
- the opening formed on the side face of the rotor 1, which consists of the Limits of sections 17, 18 is approximately oval, apart from the flat groove bottom.
- the edge lines of section 18 are arc sections of a circle, the center of which is approximately in the area of the lower end 19 of the groove side surfaces.
- Vane-camshaft adjuster Rotor wellgelnuta
- Kammerc Stator Bore Bore End section Groove side surface Undercut Groove bottom Groove groove0 End1 Transition2 Groove base3 Undercut4 Section5 Section6 Section7 Section8 Section
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004027951A DE102004027951A1 (de) | 2004-06-08 | 2004-06-08 | Flügelzellen-Nockenwellenversteller |
PCT/EP2005/005039 WO2005121511A1 (de) | 2004-06-08 | 2005-05-10 | Flügelzellen-nockenwellenversteller |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1753941A1 true EP1753941A1 (de) | 2007-02-21 |
EP1753941B1 EP1753941B1 (de) | 2008-11-26 |
Family
ID=34966652
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05739591A Expired - Fee Related EP1753941B1 (de) | 2004-06-08 | 2005-05-10 | Flügelzellen-nockenwellenversteller |
Country Status (7)
Country | Link |
---|---|
US (1) | US7588004B2 (de) |
EP (1) | EP1753941B1 (de) |
JP (1) | JP2008501886A (de) |
KR (1) | KR101179289B1 (de) |
CN (1) | CN1965149B (de) |
DE (2) | DE102004027951A1 (de) |
WO (1) | WO2005121511A1 (de) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004027950A1 (de) * | 2004-06-08 | 2006-02-16 | Ina-Schaeffler Kg | Flügelzellen-Nockenwellenversteller |
DE102007039852A1 (de) | 2007-08-23 | 2009-02-26 | Schaeffler Kg | Steuerzeitenstellvorrichtung |
US8449271B2 (en) * | 2010-05-17 | 2013-05-28 | GM Global Technology Operations LLC | Engine assembly including camshaft with integrated pump |
CN102284963A (zh) * | 2011-07-15 | 2011-12-21 | 海宁市新艺机电有限公司 | 一种旋转式剃须刀刀片及设有该刀片的剃须刀刀头 |
DE102011084944A1 (de) * | 2011-10-21 | 2013-04-25 | Schaeffler Technologies AG & Co. KG | Integration einer Axiallagerung in einen Rotor |
US9341089B2 (en) | 2014-04-04 | 2016-05-17 | RB Distribution, Inc. | Camshaft phaser |
CN103953408B (zh) * | 2014-04-30 | 2016-08-17 | 桂林电子科技大学 | 无极可变配气定时机构 |
CN105736083A (zh) * | 2014-12-12 | 2016-07-06 | 舍弗勒技术股份两合公司 | 凸轮轴相位调节器 |
CN104863656B (zh) * | 2015-06-09 | 2017-10-17 | 吕元之 | 可变气门高密度粉末冶金vvt转子及其制作方法 |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3627340B2 (ja) * | 1996-01-30 | 2005-03-09 | アイシン精機株式会社 | 弁開閉時期制御装置 |
JPH10184322A (ja) | 1996-12-24 | 1998-07-14 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
FR2769042B1 (fr) * | 1997-09-29 | 2001-11-16 | Aisin Seiki | Dispositif de reglage des soupapes |
DE19860418B4 (de) * | 1998-12-28 | 2008-09-11 | Schaeffler Kg | Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Nockenwellen-Verstelleinrichtung mit Flügelrad |
DE19962981A1 (de) * | 1999-12-24 | 2001-07-05 | Schaeffler Waelzlager Ohg | Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine insbesondere hydraulische Nockenwellen-Verstelleinrichtung in Rotationskolbenbauart |
US6247434B1 (en) * | 1999-12-28 | 2001-06-19 | Borgwarner Inc. | Multi-position variable camshaft timing system actuated by engine oil |
JP2002097911A (ja) * | 2000-09-22 | 2002-04-05 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
JP4487449B2 (ja) * | 2001-06-28 | 2010-06-23 | アイシン精機株式会社 | 弁開閉時期制御装置 |
JP4595263B2 (ja) * | 2001-07-31 | 2010-12-08 | アイシン精機株式会社 | 弁開閉時期制御装置 |
JP2003328709A (ja) * | 2002-03-08 | 2003-11-19 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
JP3906763B2 (ja) | 2002-08-28 | 2007-04-18 | アイシン精機株式会社 | 弁開閉時期制御装置 |
JP2004346788A (ja) * | 2003-05-21 | 2004-12-09 | Aisin Seiki Co Ltd | ベーン、弁開閉時期制御装置、摺動材料 |
-
2004
- 2004-06-08 DE DE102004027951A patent/DE102004027951A1/de not_active Withdrawn
-
2005
- 2005-05-10 KR KR1020067025753A patent/KR101179289B1/ko active IP Right Grant
- 2005-05-10 CN CN2005800189008A patent/CN1965149B/zh not_active Expired - Fee Related
- 2005-05-10 EP EP05739591A patent/EP1753941B1/de not_active Expired - Fee Related
- 2005-05-10 WO PCT/EP2005/005039 patent/WO2005121511A1/de active Application Filing
- 2005-05-10 US US11/570,321 patent/US7588004B2/en not_active Expired - Fee Related
- 2005-05-10 DE DE502005006071T patent/DE502005006071D1/de active Active
- 2005-05-10 JP JP2007526223A patent/JP2008501886A/ja active Pending
Non-Patent Citations (1)
Title |
---|
See references of WO2005121511A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2005121511A1 (de) | 2005-12-22 |
JP2008501886A (ja) | 2008-01-24 |
KR101179289B1 (ko) | 2012-09-03 |
CN1965149B (zh) | 2011-06-01 |
US7588004B2 (en) | 2009-09-15 |
CN1965149A (zh) | 2007-05-16 |
EP1753941B1 (de) | 2008-11-26 |
KR20070022719A (ko) | 2007-02-27 |
DE502005006071D1 (de) | 2009-01-08 |
DE102004027951A1 (de) | 2006-02-16 |
US20080047390A1 (en) | 2008-02-28 |
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