WO2001066915A2 - Verstell- und fixiereinrichtung mit klemmkörpern für eine nockenwellenverstelleinrichtung - Google Patents
Verstell- und fixiereinrichtung mit klemmkörpern für eine nockenwellenverstelleinrichtung Download PDFInfo
- Publication number
- WO2001066915A2 WO2001066915A2 PCT/AT2001/000065 AT0100065W WO0166915A2 WO 2001066915 A2 WO2001066915 A2 WO 2001066915A2 AT 0100065 W AT0100065 W AT 0100065W WO 0166915 A2 WO0166915 A2 WO 0166915A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- adjusting device
- elements
- clamping
- clamping elements
- adjusting
- Prior art date
Links
Classifications
-
- 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
- F01L1/34—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
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/26—Locking mechanisms
- F15B15/262—Locking mechanisms using friction, e.g. brake pads
Definitions
- the invention relates to an adjusting device as described in the preamble of claim 1.
- a linear adjusting device in particular a steplessly lockable cylinder, is known from DE 38 07 669 AI, the piston and thus piston rod in any position, that is stepless, locked between the two end positions and can thus be positioned in this position unlockable.
- This is achieved by a tubular design of the piston rod and a fixing device which projects into it and can be acted upon by a pressure medium, clamping elements being formed by balls.
- the disadvantage here is the additional space required for the fixing device and the large number of elements which are required for the fixing device on a working cylinder.
- An adjusting device with a clamping device for a rotating drive element is e.g. to change the control times of intake and / or exhaust valves on internal combustion engines.
- adjusting devices are known, by means of which the rotational position of a camshaft, e.g. the camshaft for the intake valves, in relation to a further camshaft and possibly in relation to the crankshaft, can be adjusted during operation according to predetermined control parameters.
- Such a device is described in DE 32 10 914 AI, a pressure medium-actuated linear drive being used to rotate a gearwheel which is rotatably connected to the camshaft and is provided with helical teeth and which meshes with an idler gear having counter-teeth, depending on the control parameters in the axial direction is adjusted and as a result of the helical teeth of the two meshing gears, the relative angular position of the gears to each other and thus the shafts in drive connection with them, for example the camshafts, or the camshaft can be changed to an intermediate shaft or the crankshaft.
- Such a device can be used in internal combustion engines in which the drive connection between the crankshaft and the camshaft or camshafts is via a
- an adjusting device with a clamping device for a camshaft control system in which on hydraulic A wheel rim for a belt or chain drive is designed to be adjustable in its rotational position relative to the wheel hub which is connected to the camshaft.
- the adjusting drive is provided in the form of a hydraulically actuatable wing arrangement, in which the wings carried by the camshaft or the hub are pivotably mounted in chambers of the wheel rim which is designed like a housing and forms pressure chambers for the wings.
- a complex control valve for pressurizing the chambers is required, whereby maintaining an exact position in the area between the end positions is difficult to achieve due to pressure fluctuations due to load, and this leads to deviations from the ideal control times negatively affect the performance of internal combustion engines.
- Means takes place and in which the position of the set rotational position is fixed by means of rolling elements which can be pressed into one another in the radial direction in the form of coil rollers and balls, which act on an element which springs open in the radial direction. In the spring-loaded state, this creates a frictional connection between the hub part and the wheel part, which can be adjusted in the rotational position relative to one another, as a result of which the set position is fixed.
- a disadvantage here are the numerous components that are subject to wear and are exposed to deformations, which increases the maintenance effort.
- the object of the invention is now to provide a hydraulically operated adjusting and fixing device which adjust the functions and the position fixing for both
- a high holding torque is achieved by moving the fixing device into the peripheral region of the drive element.
- Formations according to claims 4 and 5 are also advantageous, with the syrnme-fresh and counter-identical training achieving an identical mode of action for opposing adjustment directions.
- the supply of the pressure medium for the adjustment and fixing process is simplified and additional flow channels are eliminated.
- an embodiment according to claim 27 is also advantageous, because in this way an adjusting device for a relative movement between adjusting elements with corresponding position fixing for a linear adjusting drive is achieved, the adjustment and fixing via a common control, e.g. with a print medium. This simplifies both the control devices and the mechanical elements for such a device.
- Print medium on one side of the linear adjustment element and causes the relative adjustment between the adjustment elements without transition without further measures by the control device.
- the newly taken positions between the adjusting elements are fixed without interruption.
- Fig. 1 an adjusting device according to the invention with a fixing device for a
- Figure 2 shows the drive element, cut along lines II - II in Fig. 1.
- FIG. 3 shows a partial area of the drive element according to FIG. 1 with the fixing device according to the invention, partly in section;
- FIG. 4 shows a partial section of a further embodiment of the drive element with the adjusting device and the fixing device, partly in section;
- FIG. 6 shows another embodiment of the adjusting device and fixing device according to the invention with a partial area of the drive element, cut;
- FIG. 8 shows an internal combustion engine in a schematic representation with the adjusting device and fixing device according to the invention in view
- FIG. 9 shows a further embodiment of an adjusting device and fixing device according to the invention for a linear adjusting unit, cut according to lines IX-IX in FIG. 10;
- FIG. 11 shows another embodiment of the adjusting device, cut along the lines XI-XI in FIG. 12;
- the drive element 1 for driving a shaft 2, for example a drive shaft, control shaft, etc., which is equipped with an adjusting device 3 according to the invention and a fixing device 4 assigned to it.
- the drive element 1 is, for example, a pulley 5 in order to set the shaft 2 in rotation by means of a transmission means 6, for example a toothed belt 7.
- the drive element 1 is in two parts and consists of an actuating element 8, which forms a hub part 9, which is connected to the shaft 2 in a rotationally fixed manner, and an actuating element 10, which comprises the hub part 9, and which forms a housing-like wheel part 11.
- the hub part 9 and the wheel part 11 are relative to each other in the circumferential direction - according to double arrow 12 - adjustable by means of the adjusting device 3, whereby the angular position between the wheel part 11 and shaft 2 can be changed.
- An adjusted angular position between two adjustment processes can be fixed by means of the fixing device 4, which forms a clamping unit 13.
- the hub part 9 is provided with two diametrically opposed belt elements 15, 16 which project beyond an outer circumference 14 of the hub part 9 and which, e.g. are integrally formed on the hub part 9 and extend in the direction of an inner surface 17 of the wheel part 11 facing the hub part 9.
- a diameter 18 of an enveloping circle 19 receiving the wing elements 15, 16 is larger than an outer diameter 20 of a hub 21 of the hub part 9 and slightly smaller than an inner diameter 22 of the wheel part 11.
- the wing elements 15, 16 are conically expanded starting from the hub 21 in the direction of the enveloping circle 19, with opposite end faces 24, 25 forming planes that run at an angle to one another, whose common cutting line is approximately congruent runs with the central axis 23.
- a wheel rim 26 of the wheel part 11 has on its inner surface 17 and wall parts 27, 28 projecting above it in the direction of the hub and integrally connected to the wheel rim 26, side surfaces 29, 30 facing one another and the wing elements 15, 16 forming planes, the common thereof
- the intersection line is approximately congruent with the central axis, a center angle 31 between the planes receiving the side surfaces 29, 30 being greater than a center angle 32 of the planes receiving the end face surfaces 24, 25
- Pressure spaces 33, 34 are thus formed on both sides of the wing elements 15, 16 by the end faces 24, 25 of the wing elements 15, 16 and the side faces 29, 30 of the wall parts 27, 28, which with a pressure medium - according to the double arrow 35 - to change the relative position between Hub part 9 and wheel part 11 are optionally acted upon.
- the housing-like wheel part 11 is rotatably mounted on the hub 21 or shaft 2 and has a rear wall 36 on which the wheel rim 26 is integrally formed and on which a front wall 37 extending parallel to the rear wall 36 is fastened, between which the with the least possible play Wing elements 15, 16 are fitted, a distance 38 between mutually facing annular surfaces 39, 40 of the rear wall 36 and the front wall 37 is slightly larger than a width 41 of the wing elements 15, 16, measured in the direction of the course of the central axis 23. An almost gap-free contact of the surfaces 42, 43 of the wing elements 15, 16 opposite the ring surfaces 39, 40 is achieved.
- the rotatable mounting of the wheel element 11 with respect to the hub element 9 can take the form of a sliding bearing, roller bearing, etc., the rear wall 36 as well as the front wall
- the fixing device 4 by means of which the relative position between the hub element 9 and the wheel element 11 can be fixed, is formed from the clamping unit 13, of which at least one is arranged between the hub element 9 and the wheel element 11, for which purpose in the exemplary embodiment shown in at least one of the Wing elements 15, 16 are arranged in an end face 44 facing the inner surface 17 of the wheel rim 26, guide chambers 45, 46 for clamping elements 47, 48 arranged therein.
- the guide chambers 45, 46 are formed by depressions in the end face 44 and separated from one another by a central web 49 and delimited in the circumferential direction by side webs 50, 51.
- the guide chambers 45, 46 form support surfaces 52, 53 for the clamping elements 47, 48 opposite the inner surface 17 of the wheel rim 26.
- the guide chambers 45, 46 are thus designed to be opposite in relation to a central plane 54 running through the central web 49 and receiving the central axis 23, and the support surfaces 52, 53 run in a plane that is parallel to a surface in a line of intersection of the central plane 22 created
- Tangential plane 55 runs. An approximately conical tapering of the guide chambers 45, 46 in the direction starting from the central plane 54 is thus achieved.
- the clamping elements 47, 48 are now designed as cylindrical rolling elements 56, prestressed in opposite directions by compression springs 57 which are supported on the central web 49 and rolling elements 56, a diameter 58 of the rolling elements 56 being slightly larger than a minimum distance , but is smaller than a maximum distance between the surface 17 of the wheel rim 26 and the support surfaces 52, 53 in the region of the guide chambers 45, 46. This results in a clamping of the clamping elements 47, 48 between the support surfaces 52, 53 in the wing element 15, 16 and reached the surface 17 of the wheel rim 26 and thus prevents a relative movement between the adjusting elements 8, 10.
- FIG. 3 shows a partial area of the drive element 1 with the adjusting device 3 and the fixing device 4, on the basis of which the adjustment and fixing process is explained.
- FIG. 3 schematically shows a possible arrangement of a supply and control device 59 in a simplified configuration for the application of the adjustment direction 3 and the fixing device 4 with a pressure medium 60, for example hydraulic oil, engine oil, etc., shown.
- a pressure medium 60 for example hydraulic oil, engine oil, etc.
- this consists of a pressure vessel 61, a pressure generator 62, a control valve 63 and the corresponding supply lines 64.
- other components such as electronic monitoring elements and controls, are used where high quality is concerned
- the pressure spaces 60, 34 of the drive element 1 are acted upon by the pressure medium 60 via bores 65, 66 which are arranged in the hub 21 and which, depending on the control state, are connected as inlets or outlets.
- Various possibilities are known from the prior art for feeding the rotating hub 21 from a supply element which is fixed relative to the hub 21. 3 shows a detailed section of the drive element 1 with the wing element 15 of the hub part 9 and the drainage spaces 33, 34 delimited by the wall parts 27, 28 of the wheel part 11.
- flow channels 67 formed by bores are arranged, which on both sides of the rolling elements 56 into the guide chambers 45 , 46 open out.
- the flow channels 67 that open into the guide chambers 45, .46 along the side webs 50, 51 are inflow channels 68, while the flow channels 67 that open into the guide chambers 45, 46 along the central web form discharge channels 69.
- Spring-loaded non-return valves 70 are also arranged in these outflow channels 69, which enable the medium 60 to flow in the direction of the guide chambers 45, 46 to the bores 65, 66 and block flow in the opposite direction.
- overflow channels 71 are arranged, which the outflow channels 69 are arranged in the area between the check valves 70 and the guide chambers 45, 46, each with the two sides of the central plane 54
- the supply and control device 59 performs a loading operation. Impact with the pressure medium 60 through the bore 65 and the inflow channel 68 into the filling chamber 45. The drain structure in this causes the clamping element 47 to be displaced against the action of the compression spring 57. At the same time, a gap 73 flows between the end face 44 of the side web 50 and the inner surface 17 of the wheel rim 26, the pressure medium 60 into the pressure chamber 33 and exerts a force on the wing element 15 according to an arrow 74.
- the clamping element 47 is also flowed around, this partial quantity of the pressure medium 60 between the end face 44 of the central web 49 and the Surface 17 of the wheel rim 26 flows into the adjacent guide chamber and is discharged from there via the check valve 70 and flow channel 67. Due to the build-up of pressure in the pressure chamber 33, an adjustment movement according to arrow 72 now occurs
- Pressure chamber 34 which is opposite the pressure chamber 33 with respect to the central plane 54, existing drain medium 60 is discharged into the bore 66 via the overflow channel 71 and outflow channel 69, the check valve 70 arranged in the outflow channel 69 opening in this flow direction.
- a partial flow also flows freely through the gap 73.
- the formation of the corresponding gap dimensions is important for the rapid response of the adjusting device 3 and the fixing device 4. These can be adjusted by coordinating the outer diameter 20 of the hub 21 (see FIG. 1) with a diameter 76 of an imaginary circle, the facing end faces 77 the wall parts 27, 28 of the wheel rim 26, set.
- the gap 73 between the end face 44 of the wing element 15 and the surface 17 is determined by the diameter 18 of the enveloping circle 19 and the inner diameter 22 of the wheel rim 26.
- both the response speed for the adjustment and for the fixing, but also due to the required flow of the pressure medium 60 through the columns 73, 75 in the event of a adjusting movement achieves a damping effect in the event of load impacts that act in the direction of adjustment.
- the hub part 9 is connected in a rotationally fixed manner to the shaft 2, with at least one wing element 15 molded onto it, which is encompassed by the housing-shaped wheel part 11 and which has the projecting wall parts 27, 28 on both sides of the wing element 15 in the direction of the hub 21.
- the pressure spaces 33, 34 which are delimited in the circumferential direction by the wing element 15 and the wall parts 27, 28, are arranged on both sides of the wing element 15 projecting in the direction of the wheel rim 26.
- This configuration achieves the adjusting device 3, which further has the fixing device 4, formed by the clamping unit 13, between the wing element 15 and the wheel part 11.
- the end face 44 of the wing element 15 which faces the inner surface 17 of the wheel rim 26 is planar and at a distance 78 from the latter for receiving two by at least one drain spring arranged between them
- the wing element 15 has symmetrical to the center plane 54, the center line, salmon 23 of the shaft 2 and parallel to this in the direction of the wheel rim 26, open grooves 79, in which project as lateral holders and for the formation of drain surfaces in the direction of the surface 17 Wall parts 80, 81 are held, the grooves 79 allowing a slight pivoting movement of the wall parts 80, 81.
- the distance 78 of the end face 57 from the surface 17 tapers from the area of the central plane 54 in the opposite direction corresponding to the circular course of the surface 17.
- the maximum distance in the area of the central plane 54 is greater than a diameter 82 of the rolling elements 56 and tapers approximately corresponds to the dimension corresponding to the diameter 82. In the most distant position of the rolling elements 56 to one another, this results in the clamping action between the hub element 15 and the wheel part 11 due to the spring force of the drain spring 57.
- the maximum distance between the rolling elements 56 is determined by the wall parts 80 , 81 limited, which assume a slightly pivoted position in the wing element 15 in this position with respect to the central plane 54.
- the pressure medium 60 is fed in or out via the bores 65, 66 provided in the hub 21 via a supply device (not shown).
- the pressure medium 60 is conducted, for example, through the bore 65 into the pressure chamber 33.
- the on the wall part 80th Exerted pressure there is a pivoting this in the direction of the center plane 54 against the force of the drape spring 57 and to release the clamping action of the clamping element 47.
- the drain medium 60 to be displaced from the further pressure chamber 34 is returned to the supply system via the bore 66.
- the further clamping element 48 in the direction of movement according to arrow 83 does not oppose this movement, since this leads to a relative movement in the direction of the widening distance 78.
- relief bores 84 are provided in the wing element 15 for flow connection to the opposite drain space 33, 34. If the adjustment process is finished and the pressure is relieved, the fixing device 4 has an immediate effect due to the clamping action of the clamping elements 47, 48 due to the spring force of the pressure spring 57 acting on it.
- the drain medium 60 can be acted upon in the drain spaces 33, 34, that is to say between the wing element 15 of the grain part 9 and the wall parts 27, 28 of the wheel part 11 via the bores 65, 66 expandable liquid-tight bellows 85, 86 arranged.
- the adjustment is carried out by applying pressure to one of the pressure bellows 85, 86 with the pressure medium 60.
- FIG. 6 shows a further embodiment, in particular with regard to the design of clamping elements 47, 48 arranged in the wing element 15, 16, which in the example of FIG. 7 form approximately cuboidal clamping wedges 87, 88, which in the end face 44 of the wing - element 15 are arranged symmetrically with respect to the central plane 54 recesses 89, biased in opposite directions by one or more of the compression springs 57 and thus act clampingly between the hub part 9 and the wheel part 11.
- a displacement of the clamping wedges 87, 88 to release the fixation is, as already described in the previous example, possible by applying pressure from the pressure spaces 34, 35 which can be acted upon with the pressure medium on both sides of the wing element 15.
- the wing element 15 of the hub part 9 is comprised of separate flat pressure parts 90, 91, which with wedge-shaped extensions 92, 93 between the end face 44 of the wing element 15 and the surface 17 of the wheel rim 26 by the action of intervene between the two arranged and biasing them in the opposite direction dracking spring 57.
- the clamping action is also brought about when pressure is applied to the pressure spaces 90, 91 and the wall parts 27, 28 of the wheel part 11, which are arranged on the pressure parts 34, 35 by adjusting in the direction of the central plane 54 against the spring force of the pressure spring 57.
- FIG. 8 shows a possible application of the drive element 1 according to the invention with the adjusting device 3 and fixing device 4 ⁇ for example for a rotary drive of camshafts 94, 95 of an internal combustion engine 96.
- the drive for the cam shafts 94, 95 takes place, for example, via a belt drive, e.g. with the toothed belt 1, which drives pulleys 99, 100 arranged on the camshafts 94, 95, starting from a pulley 98 connected in a rotationally fixed manner to a crankshaft 97.
- the pulley 99 is also rotationally fixed to the camshaft 94 e.g. connected for the control of exhaust valves of the internal combustion engine 96.
- Pulley 100 for the control of intake valves is arranged at a variable angle 101 on the camshaft 95 and is adjustable relative to the latter by means of the adjusting device 3.
- the timing of the intake valves can be compared to the timing of the exhaust valves as well as the angle of rotation of the crankshaft 97 to optimize the performance of the internal combustion engine 96 under different operating conditions, e.g. adapt to the respective speed and during operation as required.
- adjustment device 3 is used is not limited to the described internal combustion engine 96.
- a position fixation of adjusting elements 8, 10 which can be adjusted relative to one another with a fixing device 4, indicated by way of illustration, with a clamping unit 13, by means of which a set relative position or the angle 101 during a predeterminable period of time or between adjustment processes during the ongoing operations can be fixed.
- a pressure cylinder 103 which can be acted upon by the pressure medium 60 consists of a cylinder jacket 104, in the exemplary embodiment shown having a circular cross section, which is closed at the ends and is provided with the connections for supply lines for the medium and which is in motion by a piston arrangement 106 connected to a piston rod 105 Drack spaces 107, 108 is divided and the piston rod 105 projects through at least one end wall 109.
- Another end wall 110 is preferably provided with a bearing block 111.
- the piston arrangement 106 has a core element 113, which is connected to the piston rod 105 at least in the direction of a longitudinal central axis 112 and is formed with respect to the longitudinal central axis 112 from a rotationally symmetrical shaped body consisting essentially of two truncated cone bodies arranged opposite one another and tapering conically towards one another.
- a cylindrical transition region 114 distances the two truncated cone bodies from one another in the region of their smaller cross-sectional area.
- the piston rod 105 is arranged comprehensively and in the longitudinal direction of the longitudinal central axis 112 by an adjustment 117 adjustable sealing disks 118, 119 are arranged.
- sealing disks 118, 119 are sealed with sealing elements 120 against the piston rod 105 and against an inner surface 121 of the cylinder jacket 104. Furthermore, the sealing disks 118, 119 have finger-like extensions 122, which surround the core element 113 on the circumference and are directed towards one another. A maximum diameter 123 of the core element 113 is at least two times the wall thickness 124 of the extensions 122 smaller than an inner diameter 125 of the cylinder jacket 104.
- the mutually facing extensions 122 are spaced apart in the circumferential direction and run in the axial direction of the drain cylinder 103 in accordance with the taper of the Kemides wedge-shaped and are supported with an inner peripheral surface 126 on the core member 113 and with an outer peripheral surface 127 on the inner surface 121 of the cylinder jacket 104.
- 11 and 12 show a further embodiment of the adjustment unit 2 according to the invention with the fixing device 4. As already described in the previous figures, this is also formed for a linear adjustment between an adjusting element 8 designed as a cylinder jacket 104 and an adjusting element 10 designed as a piston arrangement 106 with the piston rod 105. As also already described in detail, the
- Piston arrangement 106 consists of an essentially cylindrical core element 113, which comprises the piston rod 105 and is connected to it in a manner fixed in terms of movement in the direction of the longitudinal central axis 112, and the sealing discs 118, 119, which are adjustable by the adjustment path 117 in the direction of the piston rod 105 and in the direction of the longitudinal central axis 112 120 for pressure-tight sealing of the sealing washers 118, 119 from the
- the core element 113 On its outer circumference, the core element 113 has the guide chambers 45, 46 for receiving the clamping elements 47.
- the guide cams 45, 46 for example several distributed over the circumference, each have oppositely inclined support surfaces 53, by means of which a clamping action between the clamping elements arranged in the guide cams 45, 46 - solve
- sealing disks 118, 119 distributed in the circumferential direction on the extensions 122, which engage in the guide chambers 45, 46 and act on the clamping elements 47, 48 during the adjustment in order to adjust the clamping elements 47, 48 in the direction opposite the spring action in order to cancel the clamping effect ,
- FIGS. 1, 2; 3; 4; 5; 6; 7; 8th; 9, 10; 11, 12 shown form the subject of independent, inventive solutions.
- Supply and control device outer diameter 60 pressure medium hub 61 container inner diameter 62 pressure generator central axis 63 control valve end face surface 64 supply line end face surface 65 bore wheel rim 66 bore wall part 67 flow duct wall part 68 inflow duct side surface 69 outflow duct side surface 70 check valve center angle 71 overflow duct center angle 72 arrow drainage space 73 gap drainage space 74 arrow double arrow 75 gap rear wall 76 diameter front wall 77 end face distance 78 distance ring surface 79 groove ring surface 80 81 wall part 121 inner surface
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10190855T DE10190855D2 (de) | 2000-03-08 | 2001-03-08 | Verstell- und Fixiereinrichtung für eine Nockenwelle |
AU37109/01A AU3710901A (en) | 2000-03-08 | 2001-03-08 | Adjustment and locating device for a camshaft |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT3862000 | 2000-03-08 | ||
ATA386/2000 | 2000-03-08 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2001066915A2 true WO2001066915A2 (de) | 2001-09-13 |
WO2001066915A3 WO2001066915A3 (de) | 2002-04-18 |
Family
ID=3673242
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/AT2001/000065 WO2001066915A2 (de) | 2000-03-08 | 2001-03-08 | Verstell- und fixiereinrichtung mit klemmkörpern für eine nockenwellenverstelleinrichtung |
Country Status (3)
Country | Link |
---|---|
AU (1) | AU3710901A (de) |
DE (1) | DE10190855D2 (de) |
WO (1) | WO2001066915A2 (de) |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10337587A1 (de) * | 2003-08-16 | 2005-03-10 | Ina Schaeffler Kg | Hydraulischer Nockenwellenversteller mit einem Freilauf |
DE102006060676A1 (de) * | 2006-12-21 | 2008-06-26 | Schaeffler Kg | Steuerzeitenstellvorrichtung |
EP2072767A3 (de) * | 2007-12-20 | 2010-05-05 | Aisin Seiki Kabushiki Kaisha | Nockenwellenversteller |
GB2484123A (en) * | 2010-09-30 | 2012-04-04 | Mechadyne Plc | Cam summation engine valve system with variable phase operation |
WO2014029515A1 (de) * | 2012-08-20 | 2014-02-27 | Schaeffler Technologies AG & Co. KG | Befestigungsanordnung zur verbindung eines nockenwellenverstellers mit einem nockenwellenende einer nockenwelle |
DE102014208241A1 (de) * | 2014-04-30 | 2015-11-05 | Siemens Aktiengesellschaft | Druckmittelantrieb sowie Verfahren zum Betrieb eines Druckmittelantriebes |
WO2020059017A1 (ja) * | 2018-09-18 | 2020-03-26 | 三菱電機株式会社 | バルブタイミング調整装置 |
WO2020059016A1 (ja) * | 2018-09-18 | 2020-03-26 | 三菱電機株式会社 | バルブタイミング調整装置 |
WO2020084764A1 (ja) * | 2018-10-26 | 2020-04-30 | 三菱電機株式会社 | バルブタイミング調整装置 |
WO2020084763A1 (ja) * | 2018-10-26 | 2020-04-30 | 三菱電機株式会社 | バルブタイミング調整装置 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3210914A1 (de) | 1982-03-25 | 1983-09-29 | Atlas Fahrzeugtechnik GmbH, 5980 Werdohl | Nockenwellensteuergeraet |
DE3807669A1 (de) | 1988-03-09 | 1989-09-21 | Andexser Lucie | Stufenlos verriegelbarer arbeitszylinder |
DE4307010A1 (de) | 1992-03-05 | 1993-10-07 | Borg Warner Automotive | Selbstkalibrierendes, variables Nockenwellensteuersystem |
DE4311052C1 (de) | 1992-11-06 | 1994-09-15 | Ford Werke Ag | Vorrichtung zur Winkelverstellung einer Welle gegenüber ihrem Antriebsrad, insbesondere einer Nockenwelle gegenüber ihrem Nockenwellenrad |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2616973C3 (de) * | 1976-04-17 | 1981-02-19 | Wabco Fahrzeugbremsen Gmbh, 3000 Hannover | Pneumatischer Arbeitszylinder zur Betätigung und stufenlosen Arretierung von Stellgliedern |
GB2245684A (en) * | 1990-06-26 | 1992-01-08 | Ford Motor Co | Phase change mechanism. |
DE4131234A1 (de) * | 1990-09-19 | 1992-03-26 | Eaton Corp | Phasenaenderungsvorrichtung mit trennfeder |
US5540135A (en) * | 1994-12-27 | 1996-07-30 | Advanced Machine & Engineering Co. | Device for clamping an axially movable rod |
DE19719952C2 (de) * | 1997-05-14 | 2003-03-20 | Johann Weiss Maschb | Kolbenstangenbremse mit Klemmhebelsystem |
DE19846354A1 (de) * | 1998-10-08 | 2000-04-13 | Schaeffler Waelzlager Ohg | Ventilsteuerzeiten-Verstellvorrichtung für eine Brennkraftmaschine |
DE19921667A1 (de) * | 1999-05-11 | 2000-11-16 | Schaeffler Waelzlager Ohg | Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber der Kurbelwelle einer Hubkolben-Brennkraftmaschine |
-
2001
- 2001-03-08 AU AU37109/01A patent/AU3710901A/en not_active Abandoned
- 2001-03-08 WO PCT/AT2001/000065 patent/WO2001066915A2/de active Application Filing
- 2001-03-08 DE DE10190855T patent/DE10190855D2/de not_active Ceased
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3210914A1 (de) | 1982-03-25 | 1983-09-29 | Atlas Fahrzeugtechnik GmbH, 5980 Werdohl | Nockenwellensteuergeraet |
DE3807669A1 (de) | 1988-03-09 | 1989-09-21 | Andexser Lucie | Stufenlos verriegelbarer arbeitszylinder |
DE4307010A1 (de) | 1992-03-05 | 1993-10-07 | Borg Warner Automotive | Selbstkalibrierendes, variables Nockenwellensteuersystem |
DE4311052C1 (de) | 1992-11-06 | 1994-09-15 | Ford Werke Ag | Vorrichtung zur Winkelverstellung einer Welle gegenüber ihrem Antriebsrad, insbesondere einer Nockenwelle gegenüber ihrem Nockenwellenrad |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10337587A1 (de) * | 2003-08-16 | 2005-03-10 | Ina Schaeffler Kg | Hydraulischer Nockenwellenversteller mit einem Freilauf |
DE102006060676A1 (de) * | 2006-12-21 | 2008-06-26 | Schaeffler Kg | Steuerzeitenstellvorrichtung |
EP2072767A3 (de) * | 2007-12-20 | 2010-05-05 | Aisin Seiki Kabushiki Kaisha | Nockenwellenversteller |
US7921820B2 (en) | 2007-12-20 | 2011-04-12 | Aisin Seiki Kabushiki Kaisha | Valve timing control apparatus |
CN101463738B (zh) * | 2007-12-20 | 2012-10-31 | 爱信精机株式会社 | 气门正时控制装置 |
GB2484123B (en) * | 2010-09-30 | 2015-01-21 | Mechadyne Internat Ltd | Cam summation engine valve system |
GB2484123A (en) * | 2010-09-30 | 2012-04-04 | Mechadyne Plc | Cam summation engine valve system with variable phase operation |
WO2014029515A1 (de) * | 2012-08-20 | 2014-02-27 | Schaeffler Technologies AG & Co. KG | Befestigungsanordnung zur verbindung eines nockenwellenverstellers mit einem nockenwellenende einer nockenwelle |
DE102014208241A1 (de) * | 2014-04-30 | 2015-11-05 | Siemens Aktiengesellschaft | Druckmittelantrieb sowie Verfahren zum Betrieb eines Druckmittelantriebes |
WO2020059017A1 (ja) * | 2018-09-18 | 2020-03-26 | 三菱電機株式会社 | バルブタイミング調整装置 |
WO2020059016A1 (ja) * | 2018-09-18 | 2020-03-26 | 三菱電機株式会社 | バルブタイミング調整装置 |
WO2020084764A1 (ja) * | 2018-10-26 | 2020-04-30 | 三菱電機株式会社 | バルブタイミング調整装置 |
WO2020084763A1 (ja) * | 2018-10-26 | 2020-04-30 | 三菱電機株式会社 | バルブタイミング調整装置 |
Also Published As
Publication number | Publication date |
---|---|
DE10190855D2 (de) | 2004-05-27 |
AU3710901A (en) | 2001-09-17 |
WO2001066915A3 (de) | 2002-04-18 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE2909803C2 (de) | ||
DE4019221C2 (de) | Stoßdämpfer mit variabler Dämpfungskraft | |
EP0335083B1 (de) | Vorrichtung zur relativen Winkelverstellung zwischen zwei in Antriebsverbindung stehenden Wellen | |
EP0924393B1 (de) | Vorrichtung zur hydraulischen Drehwinkelverstellung einer Welle zu einem Antriebsrad | |
EP0469334B2 (de) | Vorrichtung zur Änderung der relativen Drehlage von Wellen in einer Brennkraftmaschine | |
WO1990000670A1 (de) | Antriebsvorrichtung für eine nockenwelle einer brennkraftmaschine | |
DE4410381C2 (de) | Ventiltrieb für eine Brennkraftmaschine | |
EP1076762B1 (de) | Vorrichtung zur hydraulischen drehwinkelverstellung einer welle zu einem antriebsrad | |
DE19607982C2 (de) | Nockenwellenanordnung für einen Verbrennungsmotor | |
WO2006117080A1 (de) | Verstellvorrichtung für eine brennkraftmaschine | |
WO2001066915A2 (de) | Verstell- und fixiereinrichtung mit klemmkörpern für eine nockenwellenverstelleinrichtung | |
DE4406738A1 (de) | VCT-System mit Steuerventilvorspannung bei niedrigen Drücken und nicht unter Vorspannung stehender Steuerung bei normalen Betriebsdrücken | |
DE4121475C2 (de) | Ventilzeitsteuervorrichtung für Verbrennungskraftmaschine | |
DE60220099T2 (de) | Radialkolbenhydraulikmotor | |
DE10055334C2 (de) | Vorrichtung zur relativen Drehwinkelverstellung einer Nockenwelle einer Brennkraftmaschine zu einem Antriebsrad | |
DE10105807C1 (de) | Kipphebel für einen Ventiltrieb eines Verbrennungsmotors mit Vorrichtung zur selbsttätigen Ein-/Nachstellung des Ventilspiels | |
DE10007991A1 (de) | Getriebe | |
DE102007035671B4 (de) | Schwenkmotorphasenversteller | |
DE10253883A1 (de) | Verstelleinrichtung für Nockenwellen, insbesondere von Kraftfahrzeugen | |
EP1164255A1 (de) | Vorrichtung zur relativen Drehwinkelverstellung einer Nockenwelle einer Brennkraftmaschine zu einem Antriebsrad | |
EP0924391A2 (de) | Einrichtung zur relativen Drehlagenänderung einer Welle zum Antriebsrad | |
EP1706604B1 (de) | Vorrichtung zum verändern der steuerzeiten von gaswechselven tilen einer brennkraftmaschine, insbesondere rotationskolben-verstelleinrichtung zur drehwinkelverstellung einer nockenwelle gegen ber einer kurbelwelle | |
DE4232191C1 (de) | Vorrichtung zum Verstellen der Exzentrizität eines exzentrischen Radiallagers | |
DE102007035672B4 (de) | Nockenwellenversteller | |
DE102005011452A1 (de) | Nockenwellenversteller für Brennkraftmaschinen |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A2 Designated state(s): AE AG AL AM AT AT AU AZ BA BB BG BR BY BZ CA CH CN CO CR CU CZ CZ DE DE DK DK DM DZ EE EE ES FI FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NO NZ PL PT RO RU SD SE SG SI SK SK SL TJ TM TR TT TZ UA UG US UZ VN YU ZA ZW |
|
AL | Designated countries for regional patents |
Kind code of ref document: A2 Designated state(s): GH GM KE LS MW MZ SD SL SZ TZ UG ZW AM AZ BY KG KZ MD RU TJ TM AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE TR BF BJ CF CG CI CM GA GN GW ML MR NE SN TD TG |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
DFPE | Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101) | ||
REG | Reference to national code |
Ref country code: DE Ref legal event code: 8642 |
|
AK | Designated states |
Kind code of ref document: A3 Designated state(s): AE AG AL AM AT AT AU AZ BA BB BG BR BY BZ CA CH CN CO CR CU CZ CZ DE DE DK DK DM DZ EE EE ES FI FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NO NZ PL PT RO RU SD SE SG SI SK SK SL TJ TM TR TT TZ UA UG US UZ VN YU ZA ZW |
|
AL | Designated countries for regional patents |
Kind code of ref document: A3 Designated state(s): GH GM KE LS MW MZ SD SL SZ TZ UG ZW AM AZ BY KG KZ MD RU TJ TM AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE TR BF BJ CF CG CI CM GA GN GW ML MR NE SN TD TG |
|
122 | Ep: pct application non-entry in european phase | ||
WWE | Wipo information: entry into national phase |
Ref document number: 092962001 Country of ref document: AT |
|
REF | Corresponds to |
Ref document number: 10190855 Country of ref document: DE Date of ref document: 20040527 Kind code of ref document: P |
|
WWE | Wipo information: entry into national phase |
Ref document number: 10190855 Country of ref document: DE |
|
NENP | Non-entry into the national phase |
Ref country code: JP |
|
REG | Reference to national code |
Ref country code: DE Ref legal event code: 8607 |