US20130269639A1 - Camshaft adjuster - Google Patents
Camshaft adjuster Download PDFInfo
- Publication number
- US20130269639A1 US20130269639A1 US13/994,863 US201113994863A US2013269639A1 US 20130269639 A1 US20130269639 A1 US 20130269639A1 US 201113994863 A US201113994863 A US 201113994863A US 2013269639 A1 US2013269639 A1 US 2013269639A1
- Authority
- US
- United States
- Prior art keywords
- rotor
- stator
- drive sprocket
- hydraulic channel
- camshaft phaser
- 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.)
- Abandoned
Links
Images
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
Definitions
- Vane-type adjusters have a stator, a rotor and a drive sprocket. For the most part, the rotor is nonrotatably connected to the camshaft. The stator and the drive sprocket are likewise interconnected, the rotor being disposed coaxially to and within the stator. The rotor and stator form oil chambers which can be pressurized by oil and which make possible a relative movement between the stator and rotor.
- the vane-type adjusters include various sealing covers. A plurality of screw connections are used to interconnect the stator, the drive sprocket and the sealing cover.
- a multiplicity of radially configured bores in the rotor are used for supplying oil to the oil chambers. They lead, on the one hand, into the oil chambers and, on the other hand, into the hub of the rotor; this being supplied, in turn, with oil from the end of the camshaft.
- the present invention provides a camshaft phaser has a drive sprocket, a stator and a rotor, the rotor and the stator forming two working chambers which act counter to one another to effect the rotation of the rotor relative to the stator, and the stator being torsionally fixed relative to the drive sprocket in a way that allows at least two of the aforementioned components (drive sprocket, stator and rotor) to be configured to be directly axially contiguous, and, via the formed contact surfaces thereof, to define a common hydraulic channel that leads into one of the working chambers.
- two components are configured axially contiguously. At least one of the components used has a depression. This depression may extend predominantly radially from the hub of the camshaft phaser to a first working chamber that it leads into.
- the counterpart on the other component used may feature a plane surface or likewise a depression. If both components are configured axially contiguously, then a hydraulic channel is formed in the plane of separation.
- the hydraulic channel is bounded by the contact surfaces that are configured in the immediate vicinity of the depression. These contact surfaces seal the hydraulic channel from the ambient environment.
- the camshaft phaser has a drive sprocket, a stator and a rotor, the rotor and the stator forming two working chambers which act counter to one another to effect the rotation of the rotor relative to the stator, and the stator being torsionally fixed relative to the drive sprocket, in such a way that at least two of the aforementioned components (drive sprocket, stator and rotor) are configured to be indirectly axially contiguous and to define a common hydraulic channel that leads into one of the working chambers.
- the components used for forming a hydraulic channel may be constituted of a drive sprocket, a stator, a rotor, a cover, a covering, a disk or a cap.
- the axial configuration of the components used is reminiscent of a sandwich construction of the camshaft phaser.
- the hydraulic channels formed for the respective working chambers extend substantially radially. Other hydraulic channels, for example, for supplying oil for locking or venting are conceivable in other designs.
- the hydraulic channels may be formed by depressions in one of the components.
- the depression includes corrugations, creases, hollows, slots, indentations or other recessed formations.
- hydraulic passages are formed that are substantially oil-tight relative to the ambient environment. These passages extend directly radially or, as a combination of axial and radial orientation, from an oil inflow, mostly in the hub of the camshaft phaser, to the associated working chamber.
- the cross section formed by the two components for the passage of hydraulic media is advantageously constant in shape.
- a local, specially adapted cross section for example, for forming baffles, nozzles or diffusers may be provided.
- both components may have depressions which, in combination with one another, form a fluid-conducting channel.
- two depressions which (considered in cross section) are largely semicircular, for example, are configured to form a channel, which (considered in cross section) is largely circular.
- the components used for forming a hydraulic channel are advantageously formed as a sheet-metal part, at least one component being able to have a depression.
- the depression is produced in a noncutting process by stamping, collaring, deepdrawing or extrusion.
- the depression features a constant or variable cross section of the wall thereof.
- a hydraulic channel formed leads into a first working chamber.
- This fluid-conducting connection supplies the working chamber with pressure oil in order to rotate the rotor against the stator in an advantageous direction.
- this formed oil channel may be utilized as an outlet for oil and air to evacuate the first working chamber.
- the depression enlarges the surface area, thereby promoting a transfer of heat.
- the oil is thereby adapted to the ambient temperatures.
- a stable viscosity of the oil is achieved, enabling the camshaft phaser to function with greater thermostability.
- a stiffening effect is achieved by the formation of depressions in the sheet metal of at least one of the components used.
- the stability of the component is enhanced, and material may be economized, which is beneficial in terms of achieving a lightweight construction.
- the rotor have a vane on which a recess is configured.
- This recess opens an access for hydraulic oil into a working chamber.
- the recess is advantageously formed in a rotor of sheet metal and, once joined to an axial, peripheral component, forms a fluid-conducting hydraulic channel. Alternatively, this recess may also be configured near the outer peripheral surface of the rotor.
- the recess may also be produced by punching.
- An embodiment as a sintered or cast part is also possible. Further methods include milling, turning on a lathe, erosion and other metal-cutting methods.
- One embodiment of the present invention also provides for the camshaft phaser to have a locking mechanism that couples the rotor to the stator nonrotatably.
- Two axially contiguous components are configured to form a hydraulic channel that extends from a hub of the camshaft phaser to the locking mechanism.
- FIG. 1 a section through the camshaft phaser
- FIG. 2 a cross section of FIG. 1 without a rotor
- FIG. 3 a cross section of FIG. 1 with a rotor
- FIG. 4 a further section through the camshaft phaser
- FIG. 5 a configuration including a stator, a rotor and a hub.
- FIG. 1 shows a camshaft phaser 1 , which has a drive sprocket 2 , including a nonrotatably connected stator 3 , and is concentrically configured relative to a rotor 4 .
- Drive sprocket 2 and rotor 4 are mounted on a hub 11 .
- stator 3 forms working chambers 9 , 10 which may be hydraulically pressurized. These working chambers act counter to one another and are supplied via a hydraulic channel 5 with pressure oil.
- This hydraulic channel 5 is formed by rotor 4 and drive sprocket 2 .
- Drive sprocket 2 has wall portions 2 a, 2 b of various thicknesses. Wall portions 2 a, 2 b are configured at the front end together with rotor 4 and open, respectively cover the feed lines.
- FIG. 2 shows a cross-section through FIG. 1 .
- Rotor 4 is not depicted here in order to provide a view of hydraulic channels 5 .
- the outline of wall portion 2 a whose thickness is greater is than that of wall portion 2 b, coherently follows the inner contour of stator 3 in the corresponding angular segment. This geometry is configured at least four times in the 45° angle.
- the axial offset created by the different thicknesses of wall portions 2 a and 2 b produces an axial depression, forming a hydraulic channel 5 .
- FIG. 3 shows a cross section from FIG. 1 , including rotor 4 .
- the axial contact surface of rotor 4 with drive sprocket 2 is formed in the regions of wall portions 2 a. Since rotor 4 , together with the wall thereof, extends between the wall of stator 3 and hub 11 , rotor 4 seals working chamber 9 from working chamber 10 and only allows an inflow into working chamber 10 through hydraulic channel 5 that is directly limited by rotor 4 , stator 3 and drive sprocket 2 .
- FIG. 4 shows the configuration of a camshaft phaser 1 according to FIG. 1 , including an angularly offset cross section through hydraulic-medium feed line 16 .
- rotor 4 forms a hydraulic channel 14 .
- Rotor 4 and drive sprocket 2 are axially contiguous and form contact surfaces 7 .
- recess 6 and drive sprocket 2 form a hydraulic channel 14 .
- Contact surfaces 7 seal hydraulic channel 14 , ensuring a defined position of the feed line.
- Rotor 4 also has a locking mechanism 12 . Locking mechanism 12 arrests, respectively releases rotor 4 with stator 3 in the direction of rotation of camshaft phaser 1 .
- a supplying of hydraulic oil for actuating locking mechanism 12 may be provided by an inventive design of a hydraulic channel.
- FIG. 5 shows a stator 3 having a coaxially configured rotor 4 disposed therein.
- Stator 3 and rotor 4 form working chambers 9 , 10 which act counter to one another and may be acted upon by pressure oil.
- the configuration shown here originates from camshaft phaser 1 in accordance with FIG. I and 2 .
- Rotor 4 and stator 3 are mounted on a hub 11 .
- Pressure oil, respectively hydraulic medium flows from hydraulic-medium feed line 15 of hub 11 into circumferential groove 17 and spreads over the periphery.
- the pressure oil then flows through vane 8 , which is permanently joined in one piece to rotor 4 , to recess 6 , which, together with drive sprocket 2 (not shown here), forms a hydraulic channel 14 .
- the pressure oil, respectively hydraulic medium is supplied through hydraulic channel 14 according to the present invention into working chamber 9 .
- Working chamber 10 is supplied through hydraulic channel 5 in FIG. 1 .
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
- Camshaft phasers are used in combustion engines to vary the valve timing of the combustion chamber valves. Consumption and emissions are reduced by adapting the valve timing to the actual load. One common type is the vane-type adjuster. Vane-type adjusters have a stator, a rotor and a drive sprocket. For the most part, the rotor is nonrotatably connected to the camshaft. The stator and the drive sprocket are likewise interconnected, the rotor being disposed coaxially to and within the stator. The rotor and stator form oil chambers which can be pressurized by oil and which make possible a relative movement between the stator and rotor. In addition, the vane-type adjusters include various sealing covers. A plurality of screw connections are used to interconnect the stator, the drive sprocket and the sealing cover.
- A multiplicity of radially configured bores in the rotor are used for supplying oil to the oil chambers. They lead, on the one hand, into the oil chambers and, on the other hand, into the hub of the rotor; this being supplied, in turn, with oil from the end of the camshaft.
- It is an object of the present invention to provide a camshaft phaser that has an oil guidance that is especially simple to manufacture.
- The present invention provides a camshaft phaser has a drive sprocket, a stator and a rotor, the rotor and the stator forming two working chambers which act counter to one another to effect the rotation of the rotor relative to the stator, and the stator being torsionally fixed relative to the drive sprocket in a way that allows at least two of the aforementioned components (drive sprocket, stator and rotor) to be configured to be directly axially contiguous, and, via the formed contact surfaces thereof, to define a common hydraulic channel that leads into one of the working chambers.
- To form a hydraulic channel, two components are configured axially contiguously. At least one of the components used has a depression. This depression may extend predominantly radially from the hub of the camshaft phaser to a first working chamber that it leads into. The counterpart on the other component used may feature a plane surface or likewise a depression. If both components are configured axially contiguously, then a hydraulic channel is formed in the plane of separation. The hydraulic channel is bounded by the contact surfaces that are configured in the immediate vicinity of the depression. These contact surfaces seal the hydraulic channel from the ambient environment.
- This objective is achieved in accordance with the present invention in that the camshaft phaser has a drive sprocket, a stator and a rotor, the rotor and the stator forming two working chambers which act counter to one another to effect the rotation of the rotor relative to the stator, and the stator being torsionally fixed relative to the drive sprocket, in such a way that at least two of the aforementioned components (drive sprocket, stator and rotor) are configured to be indirectly axially contiguous and to define a common hydraulic channel that leads into one of the working chambers.
- The components used for forming a hydraulic channel may be constituted of a drive sprocket, a stator, a rotor, a cover, a covering, a disk or a cap. The axial configuration of the components used is reminiscent of a sandwich construction of the camshaft phaser. The hydraulic channels formed for the respective working chambers extend substantially radially. Other hydraulic channels, for example, for supplying oil for locking or venting are conceivable in other designs.
- The hydraulic channels may be formed by depressions in one of the components. The depression includes corrugations, creases, hollows, slots, indentations or other recessed formations. When the components are joined together, hydraulic passages are formed that are substantially oil-tight relative to the ambient environment. These passages extend directly radially or, as a combination of axial and radial orientation, from an oil inflow, mostly in the hub of the camshaft phaser, to the associated working chamber. The cross section formed by the two components for the passage of hydraulic media is advantageously constant in shape. Alternatively, a local, specially adapted cross section, for example, for forming baffles, nozzles or diffusers may be provided.
- Moreover, both components may have depressions which, in combination with one another, form a fluid-conducting channel. Upon joining of the two components, two depressions, which (considered in cross section) are largely semicircular, for example, are configured to form a channel, which (considered in cross section) is largely circular.
- The components used for forming a hydraulic channel are advantageously formed as a sheet-metal part, at least one component being able to have a depression. The depression is produced in a noncutting process by stamping, collaring, deepdrawing or extrusion. The depression features a constant or variable cross section of the wall thereof.
- A hydraulic channel formed leads into a first working chamber. This fluid-conducting connection supplies the working chamber with pressure oil in order to rotate the rotor against the stator in an advantageous direction. In the case of pressure cutoff, this formed oil channel may be utilized as an outlet for oil and air to evacuate the first working chamber.
- One positive aspect is that the depression enlarges the surface area, thereby promoting a transfer of heat. The oil is thereby adapted to the ambient temperatures. Thus, a stable viscosity of the oil is achieved, enabling the camshaft phaser to function with greater thermostability.
- A stiffening effect is achieved by the formation of depressions in the sheet metal of at least one of the components used. The stability of the component is enhanced, and material may be economized, which is beneficial in terms of achieving a lightweight construction.
- One preferred embodiment of the present invention provides that the rotor have a vane on which a recess is configured. This recess opens an access for hydraulic oil into a working chamber. The recess is advantageously formed in a rotor of sheet metal and, once joined to an axial, peripheral component, forms a fluid-conducting hydraulic channel. Alternatively, this recess may also be configured near the outer peripheral surface of the rotor.
- The recess may also be produced by punching. An embodiment as a sintered or cast part is also possible. Further methods include milling, turning on a lathe, erosion and other metal-cutting methods.
- By selectively configuring the recess on the vane, it is possible to influence the flow characteristics into and out of the working chamber. These are determined by a radial positioning of the recess. In the process, a damping effect may be achieved, or a desired residual quantity of oil may remain in the working chamber.
- One embodiment of the present invention also provides for the camshaft phaser to have a locking mechanism that couples the rotor to the stator nonrotatably. Two axially contiguous components are configured to form a hydraulic channel that extends from a hub of the camshaft phaser to the locking mechanism.
- Separating an oil channel over two components, which, only when combined, form a shared oil channel along the direction of flow, makes it possible to use simple manufacturing processes and simplify quality control. Unwanted effects are also reduced, as the impurities causing them are more readily removed from crimps, corrugations, depressions and openings. Manufacturing and quality are thus significantly improved by joining a plurality of components that have the oil-conducting features.
- Exemplary embodiments of the invention are illustrated in the figures, which show:
-
FIG. 1 a section through the camshaft phaser; -
FIG. 2 a cross section ofFIG. 1 without a rotor; -
FIG. 3 a cross section ofFIG. 1 with a rotor; -
FIG. 4 a further section through the camshaft phaser; and -
FIG. 5 a configuration including a stator, a rotor and a hub. -
FIG. 1 shows acamshaft phaser 1, which has adrive sprocket 2, including a nonrotatably connectedstator 3, and is concentrically configured relative to arotor 4. Drivesprocket 2 androtor 4 are mounted on ahub 11. Together withrotor 4,stator 3forms working chambers 9, 10 which may be hydraulically pressurized. These working chambers act counter to one another and are supplied via ahydraulic channel 5 with pressure oil. Thishydraulic channel 5 is formed byrotor 4 and drivesprocket 2. Drivesprocket 2 has wall portions 2 a, 2 b of various thicknesses. Wall portions 2 a, 2 b are configured at the front end together withrotor 4 and open, respectively cover the feed lines. -
FIG. 2 shows a cross-section throughFIG. 1 .Rotor 4 is not depicted here in order to provide a view ofhydraulic channels 5. The outline of wall portion 2 a, whose thickness is greater is than that of wall portion 2 b, coherently follows the inner contour ofstator 3 in the corresponding angular segment. This geometry is configured at least four times in the 45° angle. The axial offset created by the different thicknesses of wall portions 2 a and 2 b produces an axial depression, forming ahydraulic channel 5. -
FIG. 3 shows a cross section fromFIG. 1 , includingrotor 4. The axial contact surface ofrotor 4 withdrive sprocket 2 is formed in the regions of wall portions 2 a. Sincerotor 4, together with the wall thereof, extends between the wall ofstator 3 andhub 11,rotor 4 seals working chamber 9 from workingchamber 10 and only allows an inflow into workingchamber 10 throughhydraulic channel 5 that is directly limited byrotor 4,stator 3 and drivesprocket 2. -
FIG. 4 shows the configuration of acamshaft phaser 1 according toFIG. 1 , including an angularly offset cross section through hydraulic-medium feed line 16. Together with arecess 6,rotor 4 forms a hydraulic channel 14.Rotor 4 and drivesprocket 2 are axially contiguous and form contact surfaces 7. Together,recess 6 and drivesprocket 2 form a hydraulic channel 14. Contact surfaces 7 seal hydraulic channel 14, ensuring a defined position of the feed line.Rotor 4 also has alocking mechanism 12. Lockingmechanism 12 arrests, respectively releasesrotor 4 withstator 3 in the direction of rotation ofcamshaft phaser 1. A supplying of hydraulic oil for actuatinglocking mechanism 12 may be provided by an inventive design of a hydraulic channel. -
FIG. 5 shows astator 3 having a coaxially configuredrotor 4 disposed therein.Stator 3 androtor 4form working chambers 9, 10 which act counter to one another and may be acted upon by pressure oil. The configuration shown here originates fromcamshaft phaser 1 in accordance with FIG. I and 2.Rotor 4 andstator 3 are mounted on ahub 11. Pressure oil, respectively hydraulic medium flows from hydraulic-medium feed line 15 ofhub 11 into circumferential groove 17 and spreads over the periphery. In addition, the pressure oil then flows throughvane 8, which is permanently joined in one piece torotor 4, to recess 6, which, together with drive sprocket 2 (not shown here), forms a hydraulic channel 14. The pressure oil, respectively hydraulic medium is supplied through hydraulic channel 14 according to the present invention into working chamber 9. Workingchamber 10 is supplied throughhydraulic channel 5 inFIG. 1 . - 1) camshaft phaser
- 2) drive sprocket
- 2 a, 2 b) wall portions
- 3) stator
- 4) rotor
- 5) hydraulic channel
- 6) recess
- 7) contact surface
- 8) vane
- 9) working chamber
- 10) working chamber
- 11) hub
- 12) locking mechanism
- 13) hydraulic channel
- 14) hydraulic channel
- 15) hydraulic-medium feed line
- 16) hydraulic-medium feed line
- 17) groove
Claims (7)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010063700.9 | 2010-12-21 | ||
DE201010063700 DE102010063700A1 (en) | 2010-12-21 | 2010-12-21 | Nockenellenversteller |
PCT/EP2011/066506 WO2012084284A1 (en) | 2010-12-21 | 2011-09-22 | Camshaft adjuster |
Publications (1)
Publication Number | Publication Date |
---|---|
US20130269639A1 true US20130269639A1 (en) | 2013-10-17 |
Family
ID=44658762
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/994,863 Abandoned US20130269639A1 (en) | 2010-12-21 | 2011-09-22 | Camshaft adjuster |
Country Status (4)
Country | Link |
---|---|
US (1) | US20130269639A1 (en) |
CN (1) | CN103270258B (en) |
DE (1) | DE102010063700A1 (en) |
WO (1) | WO2012084284A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20130047943A1 (en) * | 2010-02-26 | 2013-02-28 | Schaeffler Technologies AG & Co. KG | Device for variably adjusting the control times of gas exchange valves of an internal combustion engine |
US10100686B2 (en) | 2014-03-20 | 2018-10-16 | Schaeffler Technologies AG & Co. KG | Hydraulic camshaft adjuster, use, and method for assembling an at least two-part rotor of a hydraulic camshaft adjuster |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013203244A1 (en) * | 2013-02-27 | 2014-08-28 | Schaeffler Technologies Gmbh & Co. Kg | Phaser |
DE102015200145B4 (en) * | 2015-01-08 | 2021-12-30 | Schaeffler Technologies AG & Co. KG | Hydraulic camshaft adjuster with adjustable adjustment range |
US10287932B2 (en) * | 2016-09-19 | 2019-05-14 | Schaeffler Technologies AG & Co. KG | Camshaft phasing system including idler gear phaser for internal combustion engines |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5738056A (en) * | 1996-04-04 | 1998-04-14 | Toyota Jidosha Kabushiki Kaisha | Variable valve timing mechanism for internal combustion engine |
US20030033999A1 (en) * | 2001-08-14 | 2003-02-20 | Marty Gardner | Torsional assisted cam phaser for four cylinder engines having two check valves in rotor between chambers and spool valve |
US20050274344A1 (en) * | 2004-06-15 | 2005-12-15 | Jochen Auchter | Internal combustion engine having a hydraulic device for adjusting the rotation angle of a camshaft relative to a cranks haft |
US20070245991A1 (en) * | 2006-02-02 | 2007-10-25 | Schaeffler Kg | Hydraulic camshaft adjuster |
US20090159025A1 (en) * | 2007-12-20 | 2009-06-25 | Aisin Seiki Kabushiki Kaisha | Valve timing control apparatus |
US7640902B2 (en) * | 2005-06-08 | 2010-01-05 | Hydraulik-Ring Gmbh | Rotor for vane-type motor with reduced leakage |
US8307796B2 (en) * | 2007-05-02 | 2012-11-13 | Schaeffler Technologies AG & Co. KG | Camshaft adjuster for an internal combustion engine with improved design of the pressure chambers |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3745782B2 (en) * | 1993-05-03 | 2006-02-15 | ボーグワーナー・インコーポレーテッド | Internal combustion engine |
DE69702561T2 (en) * | 1996-04-03 | 2001-04-19 | Toyota Jidosha K.K., Toyota | Variable valve timing control device for internal combustion engine |
JP3211713B2 (en) * | 1996-04-04 | 2001-09-25 | トヨタ自動車株式会社 | Variable valve timing mechanism for internal combustion engine |
JP3191730B2 (en) * | 1997-07-17 | 2001-07-23 | 三菱電機株式会社 | Hydraulic valve timing adjustment device |
DE60013549T2 (en) * | 1999-12-28 | 2005-02-03 | Borgwarner Inc., Auburn Hills | Variable valve control device with a locking slide |
US7137371B2 (en) * | 2003-02-07 | 2006-11-21 | Borgwarner Inc. | Phaser with a single recirculation check valve and inlet valve |
JP4177197B2 (en) * | 2003-08-08 | 2008-11-05 | 株式会社日立製作所 | Valve timing control device for internal combustion engine |
DE102008050134B4 (en) * | 2008-10-04 | 2017-06-29 | Schaeffler Technologies AG & Co. KG | Camshaft adjustment device for an internal combustion engine |
-
2010
- 2010-12-21 DE DE201010063700 patent/DE102010063700A1/en not_active Withdrawn
-
2011
- 2011-09-22 US US13/994,863 patent/US20130269639A1/en not_active Abandoned
- 2011-09-22 WO PCT/EP2011/066506 patent/WO2012084284A1/en active Application Filing
- 2011-09-22 CN CN201180062173.0A patent/CN103270258B/en not_active Expired - Fee Related
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5738056A (en) * | 1996-04-04 | 1998-04-14 | Toyota Jidosha Kabushiki Kaisha | Variable valve timing mechanism for internal combustion engine |
US20030033999A1 (en) * | 2001-08-14 | 2003-02-20 | Marty Gardner | Torsional assisted cam phaser for four cylinder engines having two check valves in rotor between chambers and spool valve |
US20050274344A1 (en) * | 2004-06-15 | 2005-12-15 | Jochen Auchter | Internal combustion engine having a hydraulic device for adjusting the rotation angle of a camshaft relative to a cranks haft |
US7640902B2 (en) * | 2005-06-08 | 2010-01-05 | Hydraulik-Ring Gmbh | Rotor for vane-type motor with reduced leakage |
US20070245991A1 (en) * | 2006-02-02 | 2007-10-25 | Schaeffler Kg | Hydraulic camshaft adjuster |
US8307796B2 (en) * | 2007-05-02 | 2012-11-13 | Schaeffler Technologies AG & Co. KG | Camshaft adjuster for an internal combustion engine with improved design of the pressure chambers |
US20090159025A1 (en) * | 2007-12-20 | 2009-06-25 | Aisin Seiki Kabushiki Kaisha | Valve timing control apparatus |
US7921820B2 (en) * | 2007-12-20 | 2011-04-12 | Aisin Seiki Kabushiki Kaisha | Valve timing control apparatus |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20130047943A1 (en) * | 2010-02-26 | 2013-02-28 | Schaeffler Technologies AG & Co. KG | Device for variably adjusting the control times of gas exchange valves of an internal combustion engine |
US8978607B2 (en) * | 2010-02-26 | 2015-03-17 | Schaeffler Technologies AG & Co. KG | Device for variably adjusting the control times of gas exchange valves of an internal combustion engine |
US10100686B2 (en) | 2014-03-20 | 2018-10-16 | Schaeffler Technologies AG & Co. KG | Hydraulic camshaft adjuster, use, and method for assembling an at least two-part rotor of a hydraulic camshaft adjuster |
Also Published As
Publication number | Publication date |
---|---|
DE102010063700A1 (en) | 2012-06-21 |
CN103270258B (en) | 2016-08-24 |
WO2012084284A1 (en) | 2012-06-28 |
CN103270258A (en) | 2013-08-28 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20130269639A1 (en) | Camshaft adjuster | |
US9284862B2 (en) | Multi-part, joined rotors in hydraulic camshaft adjusters, having joint-sealing profiles, and method for producing the rotors | |
US20130199479A1 (en) | Rotor for a camshaft phaser, and camshaft phaser | |
JP6295720B2 (en) | Valve timing control device | |
JP5187365B2 (en) | Oil control valve | |
JP2018009577A (en) | Valve timing control device for internal combustion engine | |
JP7124775B2 (en) | Hydraulic oil control valve and valve timing adjustment device | |
US20160032792A1 (en) | Hydraulic valve and cam phaser | |
US20110197835A1 (en) | Device for the variable adjustment of valve lift curves of gas exchange valves of an internal combustion engine | |
JP6368008B2 (en) | Valve timing control device for internal combustion engine | |
JP6390499B2 (en) | Valve timing adjustment device | |
US20110000447A1 (en) | Control valve | |
US10190447B2 (en) | Camshaft adjuster and separating sleeve for a camshaft adjuster | |
JP2016079942A (en) | Valve opening/closing timing control device | |
US20150292369A1 (en) | Valve timing controller | |
JP6225750B2 (en) | Valve timing control device | |
US8978609B2 (en) | Oscillating motor adjuster | |
US20160230611A1 (en) | Hydraulic valve and cam phaser | |
WO2015079961A1 (en) | Valve opening/closing timing control device | |
JP2011202561A (en) | Valve timing control device of internal combustion engine and method of manufacturing the same | |
GB2530123A (en) | Variable valve timing control apparatus of internal combustion engine | |
JP2009215881A (en) | Valve timing adjustment device | |
US20150083066A1 (en) | Camshaft phaser system | |
US20150292368A1 (en) | Valve timing controller | |
JP2019044602A (en) | Valve timing control device for internal combustion engine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WEBER, JUERGEN;REEL/FRAME:030673/0503 Effective date: 20130410 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |
|
AS | Assignment |
Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, GERMANY Free format text: MERGER AND CHANGE OF NAME;ASSIGNORS:SCHAEFFLER TECHNOLOGIES AG & CO. KG;SCHAEFFLER VERWALTUNGS 5 GMBH;REEL/FRAME:037732/0228 Effective date: 20131231 Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, GERMANY Free format text: CHANGE OF NAME;ASSIGNOR:SCHAEFFLER TECHNOLOGIES GMBH & CO. KG;REEL/FRAME:037732/0347 Effective date: 20150101 |
|
AS | Assignment |
Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, GERMANY Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE PROPERTY NUMBERS PREVIOUSLY RECORDED ON REEL 037732 FRAME 0347. ASSIGNOR(S) HEREBY CONFIRMS THE APP. NO. 14/553248 SHOULD BE APP. NO. 14/553258;ASSIGNOR:SCHAEFFLER TECHNOLOGIES GMBH & CO. KG;REEL/FRAME:040404/0530 Effective date: 20150101 |