EP1076762A1 - Vorrichtung zur hydraulischen drehwinkelverstellung einer welle zu einem antriebsrad - Google Patents
Vorrichtung zur hydraulischen drehwinkelverstellung einer welle zu einem antriebsradInfo
- Publication number
- EP1076762A1 EP1076762A1 EP99923415A EP99923415A EP1076762A1 EP 1076762 A1 EP1076762 A1 EP 1076762A1 EP 99923415 A EP99923415 A EP 99923415A EP 99923415 A EP99923415 A EP 99923415A EP 1076762 A1 EP1076762 A1 EP 1076762A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- webs
- inner part
- pressure
- wheel
- cellular wheel
- 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
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
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
-
- 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 device for the hydraulic rotation angle adjustment of a shaft to a drive wheel, in particular the camshaft of an internal combustion engine, according to the preamble of the main claim.
- Such a device is known for example from US-A 4,858,572.
- an inner part is rotatably connected to the end of the camshaft, which has on its outside a plurality of radial slots distributed over the circumference, in which wing elements are guided radially displaceably.
- This inner part is surrounded by a cellular wheel which has a plurality of cells which can be acted upon hydraulically and which are subdivided by the wings into two pressure chambers acting against one another. By applying pressure to these pressure chambers, depending on the pressure difference, the cellular wheel can be rotated relative to the inner part and thus to the camshaft.
- a hydraulically actuated piston is guided in two radial bores in defined angular positions in the cellular wheel, which piston can be inserted into a radial recess of the inner part in the assigned end position of the device.
- These pistons are acted upon by compression spring elements in the direction of the inner part and can be displaced in the opposite direction by hydraulic action on the bores in the inner ring.
- the device is to be locked in one of its two end positions, as long as the pressure for acting on the pressure chambers does not reach a defined level. Only when a certain pressure level is reached are the pistons pushed back against the action of the compression springs and allow the inner part to be rotated relative to the cell wheel.
- the integrated hydraulic damping can be designed in a particularly advantageous manner in the form of a hydraulically effective damping throttle.
- An integrated damping which becomes effective when the respective end position is approached can be achieved in a particularly advantageous manner if a throttle chamber is formed between the webs of the inner part and the webs of the cellular wheel, in which pressure medium is enclosed before the end position is reached.
- a throttle chamber which is formed between the components that are moved relative to one another, can be used to set an angle-accurate assignment of the start of damping or a damping that begins when a defined position is reached by suitable size dimensions. This can be ensured in a particularly advantageous manner that the adjustment process takes place undamped over the largest possible angular range.
- a particularly advantageous end position damping with regard to the mechanical loading of the components results if the throttle chamber can be relieved via a defined throttle gap. Via this throttle gap, the pressure medium enclosed in the pressure chamber can be relative when approaching the end position exit strongly throttled so that excessive damping is avoided. Appropriate training of the sealing gap further ensures that the mechanically limited end position can be reached in any case. Adverse spring effects can thus be effectively prevented.
- Such a throttle chamber can be formed in a particularly advantageous manner if a depression is formed in one of the adjacent webs and a corresponding extension in the other web.
- the projection dips into the depression, so that the opposing wall regions close off the throttle chamber or form the throttle gap by their overlap.
- Fig. 1 is a view of the adjusting device facing away from the camshaft
- FIG. 2 shows a simplified section along the line II-II according to FIG. 1
- FIG. 3a shows an enlarged partial view according to FIG. 1 in a first rotational position
- FIG. 3b shows an enlarged partial view according to FIG. 1 as it approaches an end position
- Fig. 3c is an enlarged partial view of FIG. 1 when reaching the end position.
- 1 shows the camshaft of an internal combustion engine, at the free end of which the inner part 2 of an adjusting device 3 is arranged in a rotationally fixed manner.
- This inner part 2 is arranged in this embodiment with four radially Provide webs 4a to 4d.
- the inner part is encompassed by a cellular wheel 5, which is connected in a manner not shown to the crankshaft of the internal combustion engine and consequently acts as a drive wheel.
- the cellular wheel 5 is provided with four inwardly projecting radial webs 6a to 6d, between which four cells are formed which are divided into two pressure spaces 7a to 7d and 8a to 8d by the webs of the inner part.
- These pressure chambers are designed so that the sum of the hydraulically effective areas is the same in both adjustment directions.
- the pressure chambers 7a to 7d are each connected via a radial bore 9a to 9d in the inner part to an annular groove 10 on the camshaft 1.
- the pressure chambers 8a to 8d are connected in an analogous manner to a second annular groove 12 in the camshaft via radial bores 11a to 1d in the inner part.
- the radial bores 9a to 9d and 11a to 11d are each arranged in such a way that they each open into the corresponding pressure chambers in the foot region of the webs 4a to 4d.
- the two annular grooves 10 and 12 are each connected to a pressure channel 13 and 14 running in the camshaft.
- pressure channels 13 and 14 are connected in a manner known per se via a camshaft bearing 15 to a control line 16 and 17, respectively.
- the two control lines 16 and 17 are connected to a control valve 18 designed, for example, as a 4/3-way valve.
- This control valve 18 is also connected to a pressure medium pump 19 and an oil tank 20.
- the connections to the two control lines 16 and 17, the pressure medium pump 19 and the oil tank 20 are each closed on one side.
- the adjustment device is clamped hydraulically and maintains the respective relative position assignment of the inner wheel and cellular wheel.
- the pressure chambers 7a to 7d are connected to the pressure medium pump 19 via the bores 9a to 9d, the annular groove 10, the pressure channel 14 and the pressure line 17 and are accordingly pressurized.
- the pressure rooms 8a to 8d via the bores 11a to 11d, the annular groove 12, the pressure channel 13 and the pressure line 16 connected to the oil tank 20 and thus relieved.
- the inner part 2 is rotated counter-clockwise to the cell wheel 5 by the pressurization of the pressure spaces 7a to 7d in the viewing direction selected in FIG. 1. This rotation simultaneously displaces the pressure medium in the pressure chambers 8a to 8d in addition to the oil tank.
- the pressure chambers 8a to 8d are connected to the pressure medium pump and the pressure chambers 7a to 7d to the oil tank 20 via the line connections described above. This pressurization causes the inner part 2 to be rotated clockwise relative to the cell wheel.
- the cellular wheel 5 and the inner part 2 are each constructed symmetrically.
- the configuration of the webs of the inner part and the cellular wheel shown in more detail in FIGS. 3a to 3c is only shown using the example of one web or the pressure space delimited by it, but also applies equally to the other webs or pressure spaces.
- the approach to the end position analogous to the switching position I is shown and described in FIGS. 3a to 3c and the description below. Approaching the opposite end position (switch position III) takes place analogously.
- Recesses 21 and 22 are formed on the webs 6a to 6d of the cellular wheel in the region of their end facing the inner part in both side surfaces. These depressions 21, 22 extend over the entire width (in the axial direction) of the respective web.
- the depressions 21, 22 extend in the radial direction approximately over the inner third of the respective web and extend to the end face 23 or to the adjacent peripheral surface 24 of the inner part 2.
- a projection 25 and 26 are formed on the opposite sides. These projections 25 and 26 are in their position so coordinated that they correspond to the adjacent recesses 21 and 22 respectively.
- the projections 25 each interact with the depressions 22 and the projections 26 with the depressions 21 of the respectively adjacent web.
- the projections 25 and 26 also extend over the entire width (in the axial direction) of the webs. In contrast to the depressions, however, in this exemplary embodiment they do not reach the circumferential surface of the inner part, so that their undersides 27 are spaced apart from them.
- the upper sides 28 of the projections 25, 26 are at a slight radial distance from the shoulders 29 of the depressions 21 and 22, respectively, so that the projections, as can be seen in FIG. 3b, dip into the depressions while forming a throttle gap 32 can.
- the pressure spaces 8a to 8d are each divided into two partial pressure spaces 30 and 31, respectively.
- the partial pressure chamber 30 located at the foot of the webs 4a to 4d of the inner part 2 is then still connected to the bore 11a to ld respectively opening into the pressure chamber.
- the radially outer partial pressure chamber 31, which acts as a throttle chamber, is largely separated from the partial pressure chamber 30 by the covering of the upper side 28 and the shoulder 29 and is only connected to the latter via the throttle gap 32 which is established.
- the pressure medium located in the partial pressure chamber 31 can only be throttled strongly via this throttle gap 32 into the partial pressure chamber 31 and from there into the bore 11a upon further rotation up to the end position (direct abutment of the webs, FIG. 3c).
- the throttling effect that arises depends not only on the effect of the viscosity, but above all on the height and length of the throttle gap.
- the length of the throttle gap increases with increasing coverage.
- the height of the throttle gap depends on the distance between the top 28 and the shoulder 29.
- the top and the shoulder are largely parallel.
- the throttling effect therefore increases at least approximately in proportion to the increase in the overlap or the extension of the throttle gap, that is to say with increasing approach to the end position.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19819995A DE19819995A1 (de) | 1998-05-05 | 1998-05-05 | Vorrichtung zur hydraulischen Drehwinkelverstellung einer Welle zu einem Antriebsrad |
DE19819995 | 1998-05-05 | ||
PCT/EP1999/002504 WO1999057423A1 (de) | 1998-05-05 | 1999-04-14 | Vorrichtung zur hydraulischen drehwinkelverstellung einer welle zu einem antriebsrad |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1076762A1 true EP1076762A1 (de) | 2001-02-21 |
EP1076762B1 EP1076762B1 (de) | 2002-06-26 |
Family
ID=7866702
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99923415A Expired - Lifetime EP1076762B1 (de) | 1998-05-05 | 1999-04-14 | Vorrichtung zur hydraulischen drehwinkelverstellung einer welle zu einem antriebsrad |
Country Status (8)
Country | Link |
---|---|
US (1) | US6390043B1 (de) |
EP (1) | EP1076762B1 (de) |
JP (1) | JP4422899B2 (de) |
KR (1) | KR100562444B1 (de) |
CN (1) | CN1113155C (de) |
DE (2) | DE19819995A1 (de) |
ES (1) | ES2175978T3 (de) |
WO (1) | WO1999057423A1 (de) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3447601B2 (ja) * | 1999-02-05 | 2003-09-16 | 本田技研工業株式会社 | 内燃機関の動弁制御装置 |
EP1164255B1 (de) * | 2000-06-16 | 2004-03-31 | Dr.Ing. h.c.F. Porsche Aktiengesellschaft | Vorrichtung zur relativen Drehwinkelverstellung einer Nockenwelle einer Brennkraftmaschine zu einem Antriebsrad |
DE10112206A1 (de) * | 2001-03-14 | 2002-09-26 | Porsche Ag | Vorrichtung zur relativen Drehwinkelverstellung einer Nockenwelle einer Brennkraftmaschine zu einem Antriebsrad |
US6866013B2 (en) * | 2002-04-19 | 2005-03-15 | Borgwarner Inc. | Hydraulic cushioning of a variable valve timing mechanism |
DE10320639A1 (de) * | 2003-04-22 | 2004-11-11 | Hydraulik-Ring Gmbh | Nockerwellenversteller für Fahrzeuge, vorzugsweise für Kraftfahrzeuge |
US6883480B1 (en) * | 2003-12-19 | 2005-04-26 | Hydraulik-Ring Gmbh | Camshaft adjuster for internal combustion engines of motor vehicles |
DE102004019770A1 (de) * | 2004-04-23 | 2005-11-10 | Bayerische Motoren Werke Ag | Hydraulische Einrichtung zur stufenlos variablen Nockenwellenverstellung |
DE102006019607B4 (de) * | 2006-04-25 | 2008-01-31 | Hydraulik-Ring Gmbh | Nockenwellenversteller |
DE102007058491A1 (de) * | 2007-12-05 | 2009-06-10 | Schaeffler Kg | Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
JP4905843B2 (ja) * | 2010-02-23 | 2012-03-28 | 株式会社デンソー | バルブタイミング調整装置 |
US8555836B2 (en) * | 2010-12-10 | 2013-10-15 | Delphi Technologies, Inc. | Electric drive camshaft phaser with torque rate limit at travel stops |
US9341089B2 (en) | 2014-04-04 | 2016-05-17 | RB Distribution, Inc. | Camshaft phaser |
SE539977C2 (en) * | 2016-06-08 | 2018-02-20 | Scania Cv Ab | Variable cam timing phaser utilizing hydraulic logic element |
DE102018107351A1 (de) | 2017-03-28 | 2018-10-04 | Borgwarner Inc., Patent Department | Geschalteter pufferanschlag |
US10371241B1 (en) * | 2018-06-22 | 2019-08-06 | Baoxiang Shan | Stress-wave actuator and reducer |
CN114321194B (zh) * | 2021-12-30 | 2023-05-12 | 新疆金风科技股份有限公司 | 联轴节装置 |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH243908A (de) | 1944-11-27 | 1946-08-15 | Schweizerische Lokomotiv | Flüssigkeitsbremse mit Rückschlagventil am Passivkolben von hydraulisch gesteuerten Ventilen von Brennkraftmaschinen. |
DE2825326A1 (de) * | 1978-06-09 | 1979-12-20 | Daimler Benz Ag | Drehmomentuebertragungseinrichtung |
JPS59229011A (ja) | 1983-06-08 | 1984-12-22 | Yanmar Diesel Engine Co Ltd | 内燃機関の動弁機構 |
JPH0192504A (ja) * | 1987-09-30 | 1989-04-11 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
DE3922962A1 (de) * | 1989-07-12 | 1991-01-17 | Audi Ag | Antriebsvorrichtung fuer eine nockenwelle einer brennkraftmaschine |
DE4116196A1 (de) * | 1991-05-17 | 1992-11-19 | Bosch Gmbh Robert | Nockenwelle-verstellvorrichtung fuer verbrennungsmotoren |
JP2828361B2 (ja) | 1991-10-03 | 1998-11-25 | 株式会社デンソー | バルブタイミング調整装置 |
JP2988101B2 (ja) * | 1992-01-30 | 1999-12-06 | アイシン精機株式会社 | 弁開閉時期制御装置 |
DE4321003C2 (de) * | 1993-06-24 | 2001-05-03 | Schaeffler Waelzlager Ohg | Vorrichtung zum Verändern der Steuerzeiten einer Brennkraftmaschine |
IT1271511B (it) | 1993-10-06 | 1997-05-30 | Carraro Spa | Variatore di fase tra l'albero motore e l'albero a camme di un motore a combustione interna |
US5823152A (en) * | 1995-06-14 | 1998-10-20 | Nippondenso Co., Ltd. | Control apparatus for varying a rotational or angular phase between two rotational shafts, preferably applicable to a valve timing control apparatus for an internal combustion engine |
US5836276A (en) * | 1996-08-09 | 1998-11-17 | Denso Corporation | Rotational phase adjusting apparatus having fluid reservoir |
US5836277A (en) * | 1996-12-24 | 1998-11-17 | Aisin Seiki Kabushiki Kaisha | Valve timing control device |
DE19756016A1 (de) * | 1997-12-17 | 1999-06-24 | Porsche Ag | Vorrichtung zur hydraulischen Drehwinkelverstellung einer Welle zu einem Antriebsrad |
-
1998
- 1998-05-05 DE DE19819995A patent/DE19819995A1/de not_active Withdrawn
-
1999
- 1999-04-14 DE DE59901863T patent/DE59901863D1/de not_active Expired - Lifetime
- 1999-04-14 KR KR1020007012284A patent/KR100562444B1/ko not_active IP Right Cessation
- 1999-04-14 CN CN99805774A patent/CN1113155C/zh not_active Ceased
- 1999-04-14 ES ES99923415T patent/ES2175978T3/es not_active Expired - Lifetime
- 1999-04-14 EP EP99923415A patent/EP1076762B1/de not_active Expired - Lifetime
- 1999-04-14 US US09/674,707 patent/US6390043B1/en not_active Expired - Lifetime
- 1999-04-14 WO PCT/EP1999/002504 patent/WO1999057423A1/de active IP Right Grant
- 1999-04-14 JP JP2000547351A patent/JP4422899B2/ja not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO9957423A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP1076762B1 (de) | 2002-06-26 |
US6390043B1 (en) | 2002-05-21 |
DE19819995A1 (de) | 1999-11-11 |
WO1999057423A1 (de) | 1999-11-11 |
ES2175978T3 (es) | 2002-11-16 |
DE59901863D1 (de) | 2002-08-01 |
CN1113155C (zh) | 2003-07-02 |
JP4422899B2 (ja) | 2010-02-24 |
KR20010043317A (ko) | 2001-05-25 |
CN1299437A (zh) | 2001-06-13 |
KR100562444B1 (ko) | 2006-03-20 |
JP2002513883A (ja) | 2002-05-14 |
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