EP2870327A1 - Schwenkmotorversteller mit einem hydraulikventil - Google Patents
Schwenkmotorversteller mit einem hydraulikventilInfo
- Publication number
- EP2870327A1 EP2870327A1 EP13734995.7A EP13734995A EP2870327A1 EP 2870327 A1 EP2870327 A1 EP 2870327A1 EP 13734995 A EP13734995 A EP 13734995A EP 2870327 A1 EP2870327 A1 EP 2870327A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- outer diameter
- hydraulic valve
- hollow piston
- schwenkmotorversteller
- bore
- 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
- 238000009434 installation Methods 0.000 claims 1
- 239000011796 hollow space material Substances 0.000 abstract 1
- 238000007789 sealing Methods 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 8
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 239000004033 plastic Substances 0.000 description 4
- 229920003023 plastic Polymers 0.000 description 4
- 238000001746 injection moulding Methods 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 229920002430 Fibre-reinforced plastic Polymers 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000011151 fibre-reinforced plastic Substances 0.000 description 1
- 210000004907 gland Anatomy 0.000 description 1
- 239000011521 glass Substances 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000843 powder Substances 0.000 description 1
- 230000001105 regulatory effect 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
- 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
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/12—Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type
-
- 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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L2001/0475—Hollow camshafts
-
- 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
-
- 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
-
- 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
- F01L2001/34433—Location oil control valves
Definitions
- the invention relates according to claim 1 a Schwenkmotorversteller with a hydraulic valve.
- the hydraulic valve in accordance with the invention comprises a piston which is longitudinally displaceable within a bore. Go from the inner wall of the valve
- the piston has a pressure chamber inlet channel and a pressure chamber outlet channel arranged separately therefrom.
- the piston should also be made of plastic or in a design mentioned on the edge
- powder metallurgical injection molding can be produced.
- the metal injection molding process is listed.
- the pressure medium connection P is arranged axially between the two working ports A, B.
- From DE 198 53 670 B4 is also a hydraulic valve for a
- Hydraulic valve arranged pressure medium connection P leads the bore or the hollow piston from the inside pressure.
- From DE 10 2004 038 252 A1 is another hydraulic valve for a
- the object of the invention is to provide a Schwenkmotorversteller with a
- Working ports A, B are axially adjacent on a common side.
- the pressure medium connection P is immediately followed by the first working connection A (B).
- the second working connection B (A) follows this first working connection A directly or indirectly.
- "Indirect” means that there can still be a tank outlet T between the two working connections A, B.
- Working connections A, B can be at a central, for example
- Work connections A and B are arbitrary.
- the pressure medium connection P is arranged axially after or in front of the two working connections A, B.
- this pressure medium connection P outside the Schwenkmotorverstellers to channels in
- Hydraulic valve may be connected, which can promote the supply pressure of a fluid feed pump to the working ports A and B. Consequently, holes in the Schwenkmotorversteller, which conduct the supply pressure from the fluid delivery pump to the pressure medium connection P within the Schwenkmotorverstellers, not necessary. Such bores in particular by the rotor of the
- the hydraulic fluid is passed through the hollow piston of the valve.
- the hydraulic valve has a stepped bore with the outgoing from this working ports A, B on.
- Within the bore of the pressure balanced hollow piston is axially displaceable.
- the hollow piston is with a first
- the hollow piston has adjacent to this first outer diameter
- Drainage edge The two inlet edges point away from each other.
- Trailing edges face each other, so that a into a cavity of
- Circular surface is applied. This circular area is formed by the small outer diameter, so that a force in an axial direction is effective. On the other hand lies the
- K is an arbitrary constant.
- the outer diameter D1 is the small outer diameter.
- the outer diameter D2 is the large outer diameter.
- the outer diameter D3 is the first outer diameter. The said ring surface thus forms from the circular area difference at the two outer diameters D2, D3.
- bypass ports A1, B1 can also be provided.
- a method according to DE 10 2006 012 733 A1 is realized, which provides means of check valves for tank discharge flowing hydraulic fluid the Schwenkmotorversteller for pivoting movements available.
- the hydraulic valve does not have to be arranged as a central hydraulic valve radially inside the Schwenkmotorverstellers.
- Pressure medium connection P axially next to the working ports A, B instead of between the working ports A, B also brings advantages in an external or decentralized arrangement of the hydraulic valve.
- the hydraulic valve is, for example, in
- decentralized hydraulic valves usually have a fixedly coupled to the hydraulic valve electromagnetic actuator.
- Such an electromagnetic actuator has a pressure balanced magnet armature.
- the armature has a recess which connects the movement space in front of the magnet armature with the movement space behind the magnet armature.
- the armature moves in an armature interior, which is connected to the tank drain of the hydraulic valve. Since there is no significant pressure from this tank drain, the movement spaces are free of pressure and the actuator is not pushed away from the hydraulic valve.
- the hollow piston is guided axially in the stepped bore.
- This bore can be incorporated in a particularly advantageous manner in the socket of a cartridge valve.
- the bore may also be arranged in a housing.
- the bore is directly in one
- Fig. 2 is a sectional view of an electromagnetic actuator of a hydraulic valve, which finds application in a Schwenkmotorversteller and
- Fig. 3 in a sectional view of a hydraulic valve, which finds application in a Schwenkmotorversteller.
- the Schwenkmotorversteller 14 has a cylindrical stator 1 which is rotatably connected to the drive wheel 2.
- the drive wheel 2 is a sprocket over which a chain, not shown, is guided.
- the drive wheel 2 may also be a toothed belt, via which a drive belt as
- the stator 1 comprises a cylindrical stator base body 3, on the inside of which protrude webs 4 at equal intervals radially inwardly. Intermediate spaces 5 are formed between adjacent webs 4, into which pressure medium is introduced by means of a centrally arranged hydraulic valve 12 shown in more detail in FIG. 2. Between adjacent webs 4 protrude wings 6, which project radially outward from a cylindrical rotor hub 7 of a rotor 8. These wings 6 divide the spaces 5 between the webs 4 in two
- Pressure chambers 9 and 10 are assigned to the adjustment in the direction of "early", whereas the other pressure chamber is associated with the adjustment in the "late” direction.
- the webs 4 lie with their end faces sealingly against the outer circumferential surface of the rotor hub 7.
- the wings 6 in turn lie with their end faces sealingly against the cylindrical inner wall of the stator main body 3.
- the rotor 8 is rotatably connected to the camshaft 18.
- the rotor 8 is rotated relative to the stator 1.
- the pressure medium in the pressure chambers 9 or 10 is pressurized, while the respective other pressure chambers 10 or 9 are relieved to the tank T.
- the hydraulic valve 12 forms an annular first annular rotor channel 19 in the rotor hub 7 is pressurized. From this first rotor channel 19 then lead further channels 1 1 in the pressure chambers 10. This first rotor channel 19 is assigned to the first working port A.
- the hydraulic valve 12 pressurizes a second annular rotor channel 20 in the rotor hub 7, opening into the channels 13.
- This second rotor channel 20 is the second working port B
- These two rotor channels 19, 20 are arranged so as to be axially spaced relative to one another with respect to a central axis 22, so that they lie hidden one behind the other in the plane of the drawing of FIG.
- the Schwenkmotorverstellers 14 is placed on the designed as a hollow tube 16 built camshaft 18th
- the rotor 8 is placed on the camshaft 18.
- the hollow tube 16 has bores 23, 24, which are the two
- Cross holes 25, 26 connect in a socket 27 of the hydraulic valve 12.
- Hydraulic valve 12 pivotally.
- the central bore 28 within the bush 27 has two different dimensions
- the first transverse bore 25 of the bush 27 is derived from the larger inner diameter 29 and is thus assigned to the first working port A.
- the second transverse bore 26 of the bush 27 is derived from the smaller inner diameter 30 and is thus associated with the second working port B.
- a hollow piston 32 is displaceable within the sleeve 27, a hollow piston 32 is displaceable. For this purpose, the
- a plunger 35 of the electromagnetic actuator 34 is located centrally on this contact surface 33 at.
- a helical compression spring 36 on the hollow piston 32 which is supported on a support member of the bushing 27.
- the helical compression spring 36 rests against an end face 81 of the hollow piston 32.
- Hollow piston 32 has an inlet channel 37 and an outlet channel 38.
- Inlet channel 37 is a cavity 80 within the hollow piston 32 and leads via the central bore 28 in the region of the small inner diameter 30 to an axially inserted into the socket 27 pressure medium connection P.
- the drain channel 38 leads to the tank drain T. The demarcation of the inlet channel 37 from the drainage channel 38 takes place via a wall 40 within the hollow piston 32, which in the
- This oblique extension divides four control edges 41, 42, 43, 44. These control edges 41, 42, 43, 44 are arranged radially from the hollow piston 32 hinfort extending annular webs 45, 46.
- the two annular webs 45, 46 are axially spaced from each other.
- the closer to the actuator 34 annular web 45 has a lateral surface 47 with a large outer diameter D2 and is guided in the central bore 28 in the region of the larger inner diameter 29.
- the actuator 34 further standing annular web 46 has a lateral surface 48 with a small outer diameter D1 and is guided in the central bore 28 in the region of the small inner diameter 30.
- the two control edges 42, 43 define the mutually facing sides of the annular webs 45, 46.
- the two other control edges 41, 44 limit the sides facing away from each other of the annular webs 45, 46th
- the inlet channel 37 leads, however, to the two mutually remote control edges 41, 44.
- the two mutually facing control edges 42, 43 are trailing edges, whereas the control edges facing away 41st , 44 forming inlet edges.
- Run-edge control is explained in more detail in DE 198 23 619 A1.
- a first outer diameter D3 of the hollow piston 32 is slidably tolerated in a bore portion 71 tolerated.
- This bore portion 71 is formed by a sleeve 64 which is fixedly connected to the sleeve 27.
- the sleeve 64 is pressed into the socket 27.
- the first outer diameter D3 of the hollow piston 32 substantially corresponds to a first inner diameter 70 of the sleeve 64.
- the first outer diameter D3 follows in the direction from the actuator 34 to the first
- the hollow piston 32 is pressure-balanced in a particularly advantageous manner, so that position control of the Schwenkmotorverstellers 14 can be made of high quality.
- the forces acting on the hollow piston 32 axial forces cancel. That is, the left-acting force F1 in the drawing is equal to the right-acting force F2 regardless of the supply pressure at the pressure medium port P.
- This circular surface 60 is formed by the smaller outer diameter D1 of the hollow piston 32.
- the circular surface 60 is projected from an end face 81 and the obliquely extending wall 40 onto the plane perpendicular to the central axis 22.
- the opposite force F2 acts via the supply pressure at an annular surface 61 which forms from the circular surface 83 at the large outer diameter D2 minus a circular area 99 at the first outer diameter D3.
- annular surface 61 which forms from the circular surface 83 at the large outer diameter D2 minus a circular area 99 at the first outer diameter D3.
- Ring surface 61 as projected onto the plane perpendicular to the central axis 22 surface.
- the smaller inner diameter 30 of the bushing 27 corresponds essentially to the small outer diameter D1 on the lateral surface 48.
- the small outer diameter D1 essentially defines the circular surface 60, which multiplied by the pressure at the pressure medium connection P in the one axial direction - in the
- the inlet channel 37 thus establishes the hydraulic connection between the circular surface 60 and the annular surface 61.
- the circular surface 60 and the annular surface 61 have the same size for pressure equalization. For a freedom of forces is achieved, which facilitates the control of the position of the actuator, in particular in the illustrated middle position. From this middle position or blocking middle position is regulated.
- connection order or port order P-B-A-T is shown.
- the supply of the supply connection P takes place axially.
- the outflow to the tank instead of the tank drain T can be designed as a tank drain T1.
- this tank drain T1 is arranged axially between the two working ports A, B.
- the drain channel 38 to the tank outlet T also be closed according to the dashed line 87.
- the shoulder is not realized with the sleeve 64.
- another construction may be provided to enable mountability.
- the sleeve 27 may be designed as a two-part screwed component, which has a one-piece paragraph instead of the sleeve 64. The gland then ensures the mountability of the
- socket can also be provided a bore within a housing.
- the pressure medium connection P is not introduced axially into the bushing 27. Instead, the pressure medium connection P is introduced radially.
- a transverse bore or recess may be provided in the wall of the bush 27. This transverse bore is then in the axial region of the helical compression spring 36th
- the hydraulic valve can be designed according to the embodiment as a central hydraulic valve, which is also referred to as the central valve. But it can also be designed as a decentralized hydraulic valve.
- the hydraulic valve can also be designed as a cartridge hydraulic valve.
- Fig. 3 shows for a decentralized hydraulic valve 1 12 with only partially illustrated hydraulic part 1 13, the electromagnetic actuator 134.
- This actuator 134 is internally pressure balanced. Consequently, a channel 120 leads from the tank outlet T to an annular space 136 within the actuator 134 in which the armature magnet 135 is arranged axially displaceable.
- the armature magnet 135 has a recess 137, as a result of which the armature magnet 135 is pressure balanced. Since no significant pressure from the tank drain T, the movement spaces of the armature magnet 135 are free of pressure and the actuator 134 is not pressed by the hydraulic part 1 13 hinfort.
- a hydraulic part of a hydraulic valve would have a supply port P at both axial ends - e.g. in order P-B-T-A-P - pressurize the movement spaces with the supply pressure so that the actuator and the hydraulic valve would be pushed away from each other.
- the camshaft may for example be a built camshaft.
- the tank drains do not have to be arranged on the front side. So it is also possible, the tank drains as radial holes in the piston and / or in the socket
- the hydraulic valve can be designed as a central valve within the rotor hub or within a central recess of the camshaft.
- the camshaft may be a built camshaft, in which the cams are placed on a pipe.
- the pressure for the adjustment of the Schwenkmotorverstellers can come from a fluid feed pump.
- This fluid feed pump may be, in particular, the oil pump for supplying lubricant to the internal combustion engine.
- the fluid feed pump can be, if a relatively high pressure is to be applied for a high adjustment speed of the swivel motor adjuster, the fluid feed pump can
- the fluid feed pump may be designed, for example, as a vane pump.
- gear pumps may be assigned.
- the piston can be made of metal or plastic.
- the plastic is produced by injection molding. When using a plastic is also a plastic.
- Fiber-reinforced plastic advantageous, as this already in the not
- a tool with sliders can be used.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Actuator (AREA)
- Valve Device For Special Equipments (AREA)
- Fluid-Driven Valves (AREA)
- Multiple-Way Valves (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012106096.7A DE102012106096B3 (de) | 2012-07-06 | 2012-07-06 | Schwenkmotorversteller mit einem Hydraulikventil |
PCT/EP2013/063954 WO2014006056A1 (de) | 2012-07-06 | 2013-07-02 | Schwenkmotorversteller mit einem hydraulikventil |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2870327A1 true EP2870327A1 (de) | 2015-05-13 |
EP2870327B1 EP2870327B1 (de) | 2016-04-06 |
Family
ID=48771414
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13734995.7A Active EP2870327B1 (de) | 2012-07-06 | 2013-07-02 | Schwenkmotorversteller mit einem hydraulikventil |
Country Status (6)
Country | Link |
---|---|
US (1) | US9322418B2 (de) |
EP (1) | EP2870327B1 (de) |
JP (1) | JP6176656B2 (de) |
CN (1) | CN103527279B (de) |
DE (1) | DE102012106096B3 (de) |
WO (1) | WO2014006056A1 (de) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013104573B4 (de) | 2013-05-03 | 2018-05-17 | Hilite Germany Gmbh | Hydraulikventil und Schwenkmotorversteller |
DE102013104575B4 (de) | 2013-05-03 | 2018-03-08 | Hilite Germany Gmbh | Hydraulikventil und Schwenkmotorversteller |
CN104948252B (zh) * | 2014-03-28 | 2019-06-04 | 舍弗勒技术股份两合公司 | 端部供油的机油控制阀及可变气门正时系统 |
DE102014011088B3 (de) * | 2014-07-30 | 2016-01-28 | Hilite Germany Gmbh | Hydraulikventil für einen Schwenkmotorversteller |
DE102015117143B4 (de) * | 2014-10-14 | 2018-01-11 | Hilite Germany Gmbh | Nockenwellenversteller |
DE102014115903B4 (de) | 2014-10-31 | 2020-07-30 | Hilite Germany Gmbh | Hydraulikventil und Schwenkmotorversteller |
US10082054B2 (en) * | 2015-11-10 | 2018-09-25 | Delphi Technologies Ip Limited | Camshaft phaser |
DE102017124485A1 (de) * | 2017-10-19 | 2019-04-25 | Eto Magnetic Gmbh | Elektromagnetische Aktuatorvorrichtung und Verwendung einer solchen |
CN107893726A (zh) * | 2017-12-14 | 2018-04-10 | 浙江腾荣环保科技有限公司 | 一种新型液压驱动转盘 |
DE102019113713A1 (de) * | 2019-05-23 | 2020-11-26 | ECO Holding 1 GmbH | Hydraulikventil für einen Schwenkmotorversteller einer Nockenwelle |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5914664B2 (ja) * | 1981-09-30 | 1984-04-05 | 株式会社 鷺宮製作所 | 冷凍サイクル用四方逆転弁 |
DE3810804A1 (de) * | 1988-03-30 | 1989-10-19 | Daimler Benz Ag | Vorrichtung zur relativen winkelverstellung zwischen zwei in antriebsverbindung stehenden wellen |
JP3666072B2 (ja) * | 1995-09-13 | 2005-06-29 | アイシン精機株式会社 | 切替弁 |
DE19823619A1 (de) * | 1998-05-27 | 1999-12-02 | Porsche Ag | Einrichtung zur relativen Drehlagenänderung einer Welle zum Antriebsrad |
DE19853670C5 (de) * | 1998-11-20 | 2019-01-10 | Hilite Germany Gmbh | Einrichtung zur Nockenwellenverstellung |
DE102004038252A1 (de) * | 2004-05-14 | 2005-12-15 | Ina-Schaeffler Kg | Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine |
EP1596040B1 (de) * | 2004-05-14 | 2010-10-13 | Schaeffler KG | Nockenwellenversteller |
DE102004036096B4 (de) * | 2004-07-24 | 2017-09-14 | Schaeffler Technologies AG & Co. KG | Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine |
DE102005037480A1 (de) * | 2005-08-09 | 2007-02-15 | Schaeffler Kg | Steuerventil und Verfahren zur Herstellung desselben |
DE102005041393A1 (de) * | 2005-09-01 | 2007-03-08 | Schaeffler Kg | Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine |
DE102006012733B4 (de) * | 2006-03-17 | 2008-03-27 | Hydraulik-Ring Gmbh | Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement |
DE102007026831B3 (de) * | 2007-06-06 | 2008-10-02 | Hydraulik-Ring Gmbh | Elektrohydraulisches Ventil |
EP2376748B1 (de) * | 2008-12-10 | 2012-08-08 | Schaeffler Technologies AG & Co. KG | Steuerventil für eine vorrichtung zur variablen einstellung der steuerzeiten von gasaustauschventilen eines verbrennungsmotors |
EP2295740A1 (de) * | 2009-08-07 | 2011-03-16 | Delphi Technologies, Inc. | Öldurchflussregelventil für von unten zugeführtes Öl für ein Nockenwellenverstellsystem |
DE102010019005B4 (de) * | 2010-05-03 | 2017-03-23 | Hilite Germany Gmbh | Schwenkmotorversteller |
JP5187365B2 (ja) * | 2010-08-25 | 2013-04-24 | トヨタ自動車株式会社 | オイルコントロールバルブ |
DE102010060180B4 (de) * | 2010-10-26 | 2017-06-29 | Hilite Germany Gmbh | Zentralventil |
-
2012
- 2012-07-06 DE DE102012106096.7A patent/DE102012106096B3/de not_active Expired - Fee Related
-
2013
- 2013-06-13 US US13/917,095 patent/US9322418B2/en active Active
- 2013-07-02 EP EP13734995.7A patent/EP2870327B1/de active Active
- 2013-07-02 WO PCT/EP2013/063954 patent/WO2014006056A1/de active Application Filing
- 2013-07-04 JP JP2013141060A patent/JP6176656B2/ja active Active
- 2013-07-05 CN CN201310280869.1A patent/CN103527279B/zh active Active
Non-Patent Citations (1)
Title |
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See references of WO2014006056A1 * |
Also Published As
Publication number | Publication date |
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DE102012106096B3 (de) | 2014-05-15 |
CN103527279B (zh) | 2017-03-29 |
JP2014016031A (ja) | 2014-01-30 |
JP6176656B2 (ja) | 2017-08-09 |
WO2014006056A1 (de) | 2014-01-09 |
US9322418B2 (en) | 2016-04-26 |
US20140157980A1 (en) | 2014-06-12 |
EP2870327B1 (de) | 2016-04-06 |
CN103527279A (zh) | 2014-01-22 |
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