EP1197641A2 - Betätigungseinrichtung zum Festlegen einer Nockenwelle eines Antriebsmotors eines Fahrzeuges in einer Startposition - Google Patents
Betätigungseinrichtung zum Festlegen einer Nockenwelle eines Antriebsmotors eines Fahrzeuges in einer Startposition Download PDFInfo
- Publication number
- EP1197641A2 EP1197641A2 EP01123536A EP01123536A EP1197641A2 EP 1197641 A2 EP1197641 A2 EP 1197641A2 EP 01123536 A EP01123536 A EP 01123536A EP 01123536 A EP01123536 A EP 01123536A EP 1197641 A2 EP1197641 A2 EP 1197641A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- camshaft
- piston
- valve
- pressure chamber
- 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
- 230000006835 compression Effects 0.000 claims description 21
- 238000007906 compression Methods 0.000 claims description 21
- 238000007789 sealing Methods 0.000 claims description 18
- 230000002093 peripheral effect Effects 0.000 claims 1
- 238000002485 combustion reaction Methods 0.000 description 15
- 238000012432 intermediate storage Methods 0.000 description 8
- 239000007858 starting material Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 230000000903 blocking effect Effects 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 239000013013 elastic material Substances 0.000 description 1
- 239000012858 resilient material Substances 0.000 description 1
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
-
- 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
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- 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
- F01L2001/3443—Solenoid driven oil control valves
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- 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
- F01L2001/34446—Fluid accumulators for the 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
- F01L2800/00—Methods of operation using a variable valve timing mechanism
- F01L2800/01—Starting
Definitions
- the invention relates to an actuating device for setting a Camshaft of a drive motor of a vehicle, preferably of a motor vehicle, in a starting position according to the preamble of claim 1.
- the camshaft must assume a predetermined starting position. It happens that the engine is in the adjusted camshaft position comes to an abrupt stop, for example in the case of the unintentional Release the clutch at increased speed at the traffic light start. Since the Camshaft adjustment is carried out at increased speed the camshaft adjuster no longer has the time in its the lower Speed to return to the corresponding starting position. The drive motor is therefore with an adjusted camshaft. This has to Consequence that the drive motor does not start or only starts with difficulty.
- the invention is based, the generic actuator to train so that the camshaft after Switching off the drive motor reliably assumes its starting position.
- the camshaft adjusted to their starting position by a forced control and kept there. This ensures that the camshaft Switching off the engine reliably assumes its starting position.
- the The drive motor can therefore be started again without any problems.
- the Forced control is also achieved that the camshaft then too has reached the starting position required to start the engine, if, for example, by stalling the engine at elevated Speeds takes another position. If the starter is in one started in such a case, is achieved by the forced control that the camshaft reaches the start position after a short time.
- the piston rod 1 has a piston rod 1, on which a slide 2 sits.
- the piston rod 1 is at its in Fig. 1st left end with a piston 3, on which there is one end a compression spring 4 supports. It lies in a pressure chamber 5, in which opens a hydraulic line 6. It connects the pressure chamber 5 with a buffer 7, which has an overflow line 8 with a tank 9 is connected.
- In the hydraulic line 6 is in Check valve 10 opening towards pressure chamber 5.
- the slide 2 is provided with three annular grooves 11 to 13 on the circumference, which are separated from one another by ring webs 14, 15.
- the slider 2 is under the force of at least one compression spring 16, which in one Pressure chamber 17 of a valve housing 18 is housed.
- the pressure room 17 is separated from the pressure chamber 5 by a housing wall 19.
- the piston rod 1 is countered by a plunger 20 against the force of the Compression spring 4 moved.
- the plunger 20 is part of a solenoid valve 21, which in addition to the piston rod 1 also has the slide 2.
- the Ram 20 is in a known manner by a (not shown) Armature shifted when the solenoid valve 21 is energized.
- the solenoid valve 21 has two tank connections T which are connected to a common one Tank line 22 are connected to the buffer 7 ends. One sits in the tank line 22 against the intermediate store 7 opening check valve 23.
- the pressure connection P lies between the two tank connections T, to which a pressure line 24 is connected.
- the hydraulic medium is from the tank 9 via a pump 25 into the pressure line 24 promoted in a check valve closing against the tank 9 26 sits.
- the solenoid valve 21 is also with two working connections A, B Mistake.
- the working port A serves to crank a Internal combustion engine for the starting process in a starting position bring.
- the working connection B is for the adjustment of the camshaft provided with the internal combustion engine running.
- the intermediate storage 7 forms an additional one Hydraulic medium volume, which causes the piston 3 very can be quickly adjusted to the starting position shown in FIG. 1.
- the buffer store 7 is open to the atmosphere.
- the additional Hydraulic medium is the camshaft adjuster 32 at Starting process supplied enough hydraulic medium that the camshaft with the first revolutions in the start position and in this position can be locked if necessary.
- FIG. 2 shows an actuating device with which the camshaft 31 is hydraulically adjusted to a starting position.
- the camshaft is in 2 to 9 only shown schematically.
- the solenoid valve 21 is not energized in the position according to FIG. 2, so that the hydraulic medium under pressure via the pressure line 24 to the working connection A of a camshaft adjuster 32 (Fig. 10 to 12) arrives. It has pressure chambers 97 (FIG. 12) into which the hydraulic medium arrives and the camshaft 31 in still to be described Adjusted in the start position (Fig. 12). That in the unloaded Hydraulic medium located in pressure chambers 85 is over the tank line 22 and the check valve 23 in the buffer 7 ousted.
- the solenoid valve 21 switched. This causes the hydraulic medium under pressure to pass through into the pressure chambers 85 (FIGS. 11 and 12) and rotates the camshaft 31 in the opposite direction. That in the pressure rooms 97 located hydraulic medium is through the connection A and the Tank line 22 displaced back to the buffer 7.
- the solenoid valve 21 is a proportional solenoid valve so that the camshaft 31 in a wide variety of positions depending on the adjustment required can be rotated.
- the actuator 3 sits in the intermediate line 37 an electromagnetic pump 39. It has an armature 40 which is designed as a piston rod and has a piston 41 at the free end wearing. It separates two pressure spaces 42, 43 from one another in a cylinder 44. The armature 40 is in its outside of the cylinder 44 Area surrounded by a coil 45.
- the intermediate line 37 extends over the pressure space 43 into the intermediate store 7.
- the check valve 38 which blocks in the direction of the buffer memory 7.
- the actuator has the same design as the embodiment according to Fig. 2.
- the intermediate line 37 opens in accordance with the embodiment 2 in the area between the check valve 26 and the Solenoid valve 21 in the pressure line 24.
- the solenoid valve 21 is switched over.
- the pressurized hydraulic medium arrives now in the pressure chambers 85 so that the camshaft 31 in opposite directions Direction is turned.
- the one located in the pressure rooms 97 Hydraulic medium is then on the tank line 22 and that check valve 23 located therein is displaced into the intermediate store 7.
- the coil 45 is switched off, so that the armature 40 is pushed back under spring force in Fig. 3 to the left. there becomes hydraulic medium from the intermediate storage 7 in the pressure chamber 43 sucked in, so that when the internal combustion engine is switched off and switching on the pump 39 immediately as an additional volume Available.
- the solenoid valve 21 switched so that the pressure chambers 85 of the camshaft adjuster 32 with the pressure line 24 and the pressure spaces 97 of the camshaft adjuster are connected to the tank line 22.
- the coil 45 of the pump 39 is switched off, whereby the armature 40 is pushed back into the starting position shown in FIG. 4 in which the piston 41 the intermediate line 37th locks. This allows the hydraulic medium located in the pressure accumulator 49 no longer get into the pressure line 24.
- driving back of the armature 40 is that which is still in the pressure chamber 43 Hydraulic medium via the intermediate line 50 into the pressure line 24 repressed.
- the embodiment 6 is similar to that The embodiment according to FIG. 2.
- the tank 9 it has the Buffer 7, which is connected to tank 9 via overflow line 8 connected is.
- the buffer store 7 is via the intermediate line 37 connected to the pressure line 24.
- the intermediate line 37 opens in the area between the solenoid valve 21 and the camshaft 31 in the pressure line 24th
- the solenoid valve 21 switched so that the pressure chambers 85 of the camshaft adjuster 32 with the pressure line 24 and the pressure chambers 97 with the Tank line 22 is connected.
- the check valve 53 is closed, so that in the Hydraulic medium located in pressure chambers 97 is not via the intermediate line 37, but only via the tank line 22 in the buffer 7 is displaced.
- the embodiment according to FIG. 7 largely corresponds to the embodiment 3.
- the intermediate line 37 opens into Area between the solenoid valve 21 and the camshaft 31 in the pressure line 24.
- To the camshaft 31 in the start position bring, the hydraulic medium by means of the pump 25 from the Tank 9 via the pressure line 24 into the pressure chambers 97 of the camshaft adjuster 32 promoted, whereby the camshaft 31 in the Stop position is rotated.
- the electromagnetic Pump 39 turned on, so that the piston 41 in the position 7 and hydraulic medium is pushed out of the pressure chamber 43 via the intermediate line 37 into the pressure line 24 as an additional Hydraulic volume promotes. Through this additional volume the rotary movement of the camshaft 31 is in the starting position accelerated.
- the embodiment according to FIG. 9 also differs from the embodiment 5 only in that the intermediate line 50 in the area between the solenoid valve 21 and the camshaft 31 opens into the pressure line 24.
- FIGS. 8 and 9 work the same as the embodiments according to FIGS. 4 and 5.
- FIGS. 10 to 12 show the camshaft adjuster in detail 32 with which the camshaft 31 can be rotated.
- a rotary valve 54 On the cam shaft 31 rotatably sits a rotary valve 54, which is in a cylindrical Housing 55 is rotatable to a limited extent.
- the housing 55 instructs webs 56 to 60 projecting radially inward from its inner wall, which are evenly distributed over the circumference and end faces 61 to 65 with which they are flat on the cylindrical outer jacket 66 of the rotary valve 54 abut.
- the rotary slide valve 54 protrudes radially beyond the outer jacket 66 Arms 67 to 71, which protrude between the webs 56 to 60 and with their curved faces 72 to 76 flat on the cylindrical inside 77 of the housing 55 abut.
- the measured in the circumferential direction Width of arms 67 to 71 is less than the distance between adjacent webs 56 to 60.
- the housing 55 has two annular ones lying parallel to one another Cover 78, 79 (Fig. 10), between which the rotary valve 54 is located. At the outer edge, the two covers 78, 79 are by a ring 80 connected to each other, the cylindrical inside 77 of the housing 55 has. The two covers 78, 79 lie on the two Side surfaces of the rotary valve 54.
- the rotary valve 54 sits on a threaded bolt 81 with which the Rotary slide valve 54 is attached with one end 82 of the camshaft 31 becomes.
- the camshaft end 82 protrudes through the housing cover 78 to about half the axial width of the rotary valve 54.
- the rotary valve 54 has a smaller wall thickness than in the area outside the camshaft end 82 (FIGS. 11 and 12). It is provided with a central, axial bore 83 in which radially extending bores passing through the rotary valve 54 84 (Fig. 11) open. They connect the central bore 83 with each a pressure chamber 85, each of the web 56 to 60 and the adjacent arm 67 to 71 is limited.
- Fig. 11 radially extending bores passing through the rotary valve 54
- FIG. 11 shows the rotary valve 54 in one stop position, in which his arms 67 to 71 bear against the left-hand side walls of the webs 56 to 60 in FIG. 11.
- the webs 56 to 60 are on both sides with Provided projections 86 and 87 extending circumferentially, on which the arms 67 to 71 of the rotary valve 54 rest. These projections 86, 87 ensure that in FIG. 11 Stop position shown, the holes 84 through the webs 56th until 60 are not completely closed.
- the axial bore 83 of the distributor 82 is via a transverse bore 88 connected to an annular groove 89 in the outer jacket of the camshaft end 82 provided and radially by a ring 90 is limited outside.
- a bore 91 opens into the annular groove 89 which the hydraulic medium from the tank 9 or from the intermediate storage 7 is supplied.
- the camshaft end 82 is on its outer lateral surface a further annular groove 92 (FIG. 10), which is formed by the ring 90 is closed radially outwards and into which a bore 93 opens.
- An axial bore 94 is also connected to the annular groove 92, which opens into an annular groove 95 in the camshaft end 82.
- radially penetrating Bores 96 in the thinner wall area of the rotary valve 54 are provided and open into the pressure chambers 97, which between the webs 56 to 60 of the housing 55 and the arms 67 to 71 of the Rotary valve 54 lie.
- the pressure rooms 85 and 97 are through Arms 67 to 71 of the rotary valve 54 separated from each other.
- Fig. 13 shows a solenoid valve 21a, the plunger 20a on one Pressure piston 98 abuts.
- a dome-shaped head 99 is the Pressure piston 98 on a resilient plate 100, which in the exemplary embodiment made of rubber-elastic material or rubber can exist.
- the plate 100 is on its periphery in the housing 18a clamped.
- a socket 101 is inserted into the housing 18a, secured with a snap ring 102 in the housing 18a is.
- the plate 100 is between that facing away from the locking ring 102 End of the bushing 101 and a radial shoulder surface 103 clamped, which protrudes from the inner wall of the housing 18a.
- the Bushing 101 has a bottom 104 that extends from at least one bore 105, in the exemplary embodiment of two bores 105, axially penetrated is.
- the bores 105 are on their from the locking ring 102 opposite end closed by a valve plate 106 which with a screw 107 fastened to the bottom 104 of the socket 101 is.
- the valve plate 106 is elastic at least in the edge area compliantly trained.
- the bores 105 are connected to the hydraulic line 6 (FIG. 1), via which the hydraulic medium from the intermediate storage is fed. Is located between the plate 100 and the valve plate 106 the pressure chamber 5a.
- the socket 101 and the wall the housing 18a is provided with transverse bores 108, 109 which cursed with each other.
- the transverse bores 108 of the bush 101 are closed by a ring 110 which is elastically expandable and in an annular groove 111 housed in the outer wall of the socket 101 is.
- the solenoid valve 21a basically works in the same way as it does has been described with reference to the embodiment of FIG. 1.
- the plunger 20a of the solenoid valve 21a by turning on Solenoid valve in Fig. 13 shifted to the left, is over the pressure piston 98 the plate 100 resiliently in the direction of the valve plate 106 deformed.
- the hydraulic medium located in the pressure chamber 5a put under pressure.
- This pressure turns the ring 110 elastically expanded so that the hydraulic medium over the now open Cross bores 108 from the pressure chamber 5a through the cross bores 109 can flow to the respective work connection.
- the valve plate 106 is firmly in its Fig. 13 shown closed position, so that the hydraulic medium cannot get into the holes 105. This will make the Camshaft 31 rotated into the starting position in the manner described.
- the solenoid valve 21b the plunger 20b, which acts on the piston 3b. It is in an axial bore 112 of the valve housing 18b out.
- the pressure chamber 5b is through the piston 3b and a bottom 113 of the valve housing 3b axially limited.
- At least two transverse bores open into the pressure chamber 5b 114 and 115, which are provided in the valve housing 18b.
- the transverse bore 115 is connected to the hydraulic line 6 (FIG. 1), via which the hydraulic medium from the intermediate storage 7 is conveyed into the pressure chamber 5b.
- the pressure port P (Fig. 1) is connected.
- each of the two transverse bores 114, 115 there is a bush 116, 117.
- the bottom 118, 119 of the bushings 116, 117 is each with a central through opening 120, 121 provided.
- the passage opening 120 of the socket 116 faces the pressure chamber 5b, while the through hole 121 of the bushing 117 from the pressure chamber 5b is turned away.
- a flow distributor is located in each of the two bushings 116, 117 124, 125 inserted, which has star-shaped arms 126, 127, between which the hydraulic medium in the pressure chamber 5b or out the pressure chamber 5b can flow.
- the arms 126, 127 are radial from the upper end of a central body 128, 129, which with Distance is surrounded by the socket 116, 117. Arms 126, 127 the flow distributors 124, 125 sit on a radial shoulder surface 130, 131 on the inside of the bushings 116, 117 and are attached to it in a suitable manner. It is also possible to use the arms 126, 127 to be pressed into the sockets 116, 117.
- the passage opening 121 is connected to the hydraulic line 6 (FIG. 1), through which the hydraulic medium described in the Way can get into the pressure chamber 5b.
- the Valve plate 123 from the bottom 119 of the sleeve 117, so that the hydraulic medium between the arms 127 of the flow distributor 125 can get into the pressure chamber 5b.
- the 15 has the plunger 20c, which on the Piston 3c acts. It is on the inner wall over part of its length guided a bushing 132 which in the axial bore 112c of the Valve housing 18c is used.
- the piston 3c is on its from End face facing away from plunger 20c with a central recess 133 provided, in which one end of a compression spring 4c engages. Your other End sits in a central recess 134 of a cup-shaped Recording 135, which has an end flange 136 between the Bottom 113c of the valve housing 18c and one on the socket 132 adjacent ring 141 is clamped.
- the socket 132 surrounds the Recording 135 at a distance, so that between the socket and the Recording an annular space 137 is formed by the hydraulic medium flow into the pressure chamber 5c in a manner to be described can.
- Another annular space 138 is between the bushing 132 and formed part of the length of the piston 3c.
- the annular spaces 137 and 138 each open over the circumference of the Valve housing 18c distributed through bores 139 and 140, which the valve housing 18c and the sleeve 132 radial push through.
- Two rings 141, 142 are inserted into the socket 132, with which the sealing rings 143 to 145 are secured in the inner wall the socket 132 are arranged and fixed in it.
- In height of the through bores 139, 140 are the two rings 141, 142 provided with appropriate holes.
- the sealing ring 143 lies with Distance from flange 136 of receptacle 135 and seals the annulus 137 against the pressure chamber 5c.
- the annular space 138 is separated from one another by the two lying sealing rings 144 and 145 limited, of which the Sealing ring 144 seals the annular space 138 against the pressure space 5c.
- the sealing lips of the two sealing rings 144, 145 are inclined in the direction facing each other.
- Fig. 16 shows a solenoid valve 21d
- the plunger 20d of the piston 3d is applied. It is axial over part of its length in bushing 132d guided. It has one at its end facing the plunger 20d radially outward flange 146 with which it is connected to a radial Shoulder surface 147 on the inside of the valve housing 18d is applied.
- the solenoid valve 21d has a central base 148, the axially according to the previous embodiments the housing part 149 of the magnetic part of the solenoid valve 21d axially protrudes.
- the projecting end of the base body 148 is mushroom-shaped educated. On this protruding end is the valve housing 18d positively placed over a flange.
- the flange 146 of the socket 132d is between the shoulder surface 147 and the End of the protruding end of the base body 148 clamped.
- auxiliary piston 150 sits on the piston 3d, which is on the socket 146 facing away from a radially outward flange 151 has. With it, the auxiliary piston 150 is not energized Solenoid valve 21d on a radially inward shoulder surface 152, which on the inner wall of the axial bore 112d of Valve housing 18d is provided under the force of the compression spring 16d on. It is also supported on the face of the socket 132d from.
- the piston 3d is under the force of the compression spring 4d with a End at a flow body 153 and at its other end an inner radial shoulder surface 154 is supported in the piston 3d is.
- the flow body 153 is of the same design as the flow distributor 124, 125 and has radially from one end of the body 155 protruding arms 156 which are spaced apart and thereby form passages for the hydraulic medium.
- the Arms 156 lie on a radial shoulder surface 157 on the inner wall the bore 112d of the valve housing 18d.
- the basic body 155 is spaced from the inner wall of the valve housing 18d surround, creating an annular space 158 between the base body 155 and the inner wall of the valve housing 18d is formed.
- a bore 159 opens out into the center of the annular space 158 113d of the valve housing 18d.
- the bore 159 is through the valve plate 160 closed, which consists of resilient material and attached to the floor 113d so that it is released the hole 159 can bend away elastically.
- the auxiliary piston 150 delimits an annular space 161 radially inwards, the radially outward through the wall of the valve housing 18d is limited.
- the wall of the valve housing opens into this annular space 161 18d radially penetrating through bores 162.
- the solenoid valve 21d If the solenoid valve 21d is not energized, the auxiliary piston 150 is underneath sealing the force of the compression spring 16d on the shoulder surface 152 on. As a result, the annular space 161 is separated from the pressure space 5d lies between the piston 3d and the flow body 153.
- the Valve plate 160 closes the axial bore 159. Will the solenoid valve 21d energized, the plunger 20d pushes the piston 3d against the force of the compression spring 4d, whereby that in the pressure chamber 5d Hydraulic medium is pressurized. This pressure is greater than that exerted on the auxiliary piston 150 by the compression spring 16d Counterforce, so that the auxiliary piston 150 by the hydraulic medium is pushed back.
- the described solenoid valves 21a to 21d according to FIGS. 13 to 16 can be used in the setting devices according to FIGS. 1 to 9 become.
- the solenoid valves 21a to 21d can of course also be used wherever medium sucked in and fed to a consumer under pressure should.
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
- Fig. 1
- eine erfindungsgemäße Betätigungseinrichtung,
- Fig. 2 bis Fig. 9
- jeweils Hydraulikpläne von erfindungsgemäßen Betätigungseinrichtungen,
- Fig. 10
- einen Axialschnitt durch einen Nockenwellenversteller, der durch die erfindungsgemäße Betätigungseinrichtung betätigt wird,
- Fig. 11
- einen Schnitt längs der Linie A-A in Fig. 10,
- Fig. 12
- einen Schnitt längs der Linie B-B in Fig. 10,
- Fig. 13 bis Fig. 16
- verschiedene Ausführungsformen von Magentventilen der erfindungsgemäßen Betätigungseinrichtung.
Claims (33)
- Betätigungseinrichtung zum Festlegen einer Nockenwelle eines Antriebsmotors eines Fahrzeuges, vorzugsweise eines Kraftfahrzeuges, in einer Startposition,
dadurch gekennzeichnet, daß die Nockenwelle (31) durch eine Zwangsteuerung in ihre Startposition verstellbar ist. - Einrichtung nach Anspruch 1,
dadurch gekennzeichnet, daß die Nockenwelle hydraulisch in ihre Startposition verstellbar ist. - Einrichtung nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß die Einrichtung zur Verstellung der Nockenwelle (31) ein Magnetventil (21, 21a bis 21d) aufweist, mit dem der Zufluß eines Druckmediums, vorzugsweise Hydraulikmediums, steuerbar ist. - Einrichtung nach einem der Ansprüche 1 bis 3,
dadurch gekennzeichnet, daß mit der Einrichtung ein Drehschieber (54) eines Nockenwellenverstellers (32) betätigbar ist, und daß der drehfest mit der Nockenwelle (31) verbundene Drehschieber (54) wenigstens einen Kolben (67 bis 71) aufweist, der beidseitig mit dem Druckmedium beaufschlagbar ist. - Einrichtung nach Anspruch 4,
dadurch gekennzeichnet, daß dem Druckmedium zur Verstellung des Kolbens (67 bis 71) ein Zusatzvolumen an Druckmedium zuführbar ist, das vorteilhaft in wenigstens einem vorzugsweise zur Atmosphäre offenen Zusatzspeicher (7, 49) untergebracht ist. - Einrichtung nach Anspruch 5,
dadurch gekennzeichnet, daß der vorteilhaft als Druckspeicher ausgebildete Zusatzspeicher (7) über wenigstens eine Überlaufleitung (8) mit einem Tank (9) des Druckmediums verbunden ist. - Einrichtung nach Anspruch 5 oder 6,
dadurch gekennzeichnet, daß dem Zusatzspeicher (7, 49) wenigstens eine vorteilhaft elektromagnetisch ausgebildete Pumpe (39) nachgeschaltet ist, die vorzugsweise einen Kolben (41) aufweist, mit dem das Zusatzvolumen dem Druckmedium zuführbar ist. - Einrichtung nach Anspruch 7,
dadurch gekennzeichnet, daß der Kolben (41) der Pumpe (39) eine Zuleitung (37) für das Zusatzvolumen in einer Ausgangslage schließt. - Einrichtung nach einem der Ansprüche 4 bis 8,
dadurch gekennzeichnet, daß das Druckmedium aus dem Nokkenwellenversteller (32) nach dem Starten des Antriebsmotors und Umschalten des Magnetventils (21) in den Zusatzspeicher (7) zurückführbar ist. - Einrichtung, insbesondere nach einem der Ansprüche 1 bis 9,
dadurch gekennzeichnet, daß die Einrichtung einen Schieber (2) aufweist, der auf einer Kolbenstange (1) angeordnet ist. - Einrichtung nach Anspruch 10,
dadurch gekennzeichnet, daß die Kolbenstange (1) relativ zum Schieber (2) verschiebbar ist, der vorteilhaft durch einen Anschlag (30) auf der Kolbenstange (1) gegen eine Gegenkraft, vorzugsweise eine Federkraft verschiebbar ist. - Einrichtung nach Anspruch 10 oder 11,
dadurch gekennzeichnet, daß der Schieber (2) und die Kolbenstange (1) Teil des Magnetventils (21) sind. - Einrichtung nach einem der Ansprüche 10 bis 12,
dadurch gekennzeichnet, daß die Kolbenstange (1) einen Kolben (3) trägt, der in einer Ausgangsstellung unter Kraft an einem gehäuseseitigen Anschlag (19) des Magnetventils (21) anliegt. - Einrichtung nach einem der Ansprüche 4 bis 13,
dadurch gekennzeichnet, daß der Drehschieber (54) in einem Gehäuse (55) begrenzt drehbar ist und vorteilhaft als Kolben mehrere radial abstehende Arme (67 bis 71) aufweist. - Einrichtung nach Anspruch 14,
dadurch gekennzeichnet, daß das Gehäuse (55) wenigstens einen, vorzugsweise mehrere radial nach innen ragende Stege (56 bis 60) aufweist, zwischen welche die Arme (67 bis 71) des Drehschiebers (54) eingreifen. - Einrichtung nach einem der Ansprüche 4 bis 15,
dadurch gekennzeichnet, daß der Kolben (67 bis 71) des Drehschiebers (54) zwei Druckräume (85, 97) voneinander trennt, die zwischen dem Kolben (67 bis 71) des Drehschiebers (54) und dem Steg (56 bis 60) des Gehäuses (55) liegen. - Einrichtung nach einem der Ansprüche 4 bis 16,
dadurch gekennzeichnet, daß das Druckmedium axial über wenigstens eine Bohrung in der Nockenwelle (31) dem Nockenwellenversteller (32) zuführbar ist. - Einrichtung nach einem der Ansprüche 15 bis 17,
dadurch gekennzeichnet, daß der Steg (56 bis 60) wenigstens einen Vorsprung (86, 87) aufweist, an dem der Arm (67 bis 71) des Drehschiebers (54) zur Anlage kommt. - Einrichtung nach einem der Ansprüche 4 bis 18,
dadurch gekennzeichnet, daß der Drehschieber (54) axial gesichert zwischen zwei vorteilhaft am umfangsseitigen Rand durch einen Ring (80) miteinander verbundenen Deckeln (78, 79) des Gehäuses (55) liegt. - Einrichtung, insbesondere nach einem der Ansprüche 1 bis 19,
dadurch gekennzeichnet, daß sie ein Magnetventil (21, 21a bis 21d) aufweist, dessen Ventilteil als Pumpe ausgebildet ist. - Einrichtung nach Anspruch 20,
dadurch gekennzeichnet, daß das Druckmedium in wenigstens einem Druckraum (5, 5a bis 5d) unter Druck gesetzt und wenigstens einem Arbeitsanschluß (A, B; 109; 120; 140; 162) zugeführt wird. - Einrichtung nach Anspruch 20 oder 21,
dadurch gekennzeichnet, daß das Druckmedium in den Druckraum (5, 5a bis 5d) mittels Unterdruck förderbar ist. - Einrichtung nach einem der Ansprüche 20 bis 22,
dadurch gekennzeichnet, daß das Magnetventil (21a) einen Kolben (98) aufweist, mit dem bei Bestromen des Magnetventils wenigstens ein den Druckraum (5a) begrenzendes, vorteilhaft durch den Kolben (98) elastisch verformbares Druckelement (100) zur Erzeugung des Druckes im Druckraum (5a) verstellbar ist. - Einrichtung nach Anspruch 23,
dadurch gekennzeichnet, daß in den Druckraum (5a) wenigstens eine Bohrung (105) mündet, über die das Druckmedium zuführbar ist und die durch ein vorteilhaft unter dem Unterdruck von der Bohrung (105) abhebendes Ventilelement (106) verschließbar ist. - Einrichtung nach Anspruch 24 oder 25,
dadurch gekennzeichnet, daß das Ventilelement (106) zur Freigabe der Bohrung (105) elastisch verformbar ist. - Einrichtung nach einem der Ansprüche 20 bis 22,
dadurch gekennzeichnet, daß in den Druckraum (5b) wenigstens eine Zuführöffnung (121) und wenigstens ein Arbeitsanschluß (120) münden, die jeweils durch ein Ventilelement (122, 123) verschließbar sind. - Einrichtung nach Anspruch 26,
dadurch gekennzeichnet, daß die vorteilhaft elastisch verformbaren Ventilelemente (122, 123) so angeordnet sind, daß bei Druckbeaufschlagung des Druckmediums das dem Arbeitsanschluß (120) zugeordnete Ventilelement (122) und bei Unterdruck im Druckraum (5b) das der Zuführöffnung (121) zugeordnete Ventilelement (123) in eine Offenstellung bewegbar sind. - Einrichtung nach einem der Ansprüche 20 bis 22,
dadurch gekennzeichnet, daß der Druckraum (5c) durch jeweils wenigstens eine, vorteilhaft als Radialwellendichtring ausgebildete Dichtung (143, 144) gegen wenigstens eine Zuführöffnung (139) und wenigstens einen Arbeitsanschluß (140) abgedichtet ist, und daß vorzugsweise die dem Arbeitsanschluß (140) zugeordnete Dichtung (144) am Kolben (3c) dichtend anliegt. - Einrichtung nach Anspruch 28,
dadurch gekennzeichnet, daß die Dichtungen (143, 144) so angeordnet sind, daß bei Druckbeaufschlagung des Druckmediums im Druckraum (5c) die dem Arbeitsanschluß (140) zugeordnete Dichtung (144) und bei Unterdruck im Druckraum (5c) die der Zuführöffnung (139) zugeordnete Dichtung (143) in eine den Durchtritt des Druckmediums ermöglichende Lage bewegbar ist. - Einrichtung nach einem der Ansprüche 20 bis 22,
dadurch gekennzeichnet, daß der Arbeitsanschluß (162) durch einen vorzugsweise auf dem Kolben (3d) verschiebbar gelagerten Hilfskolben (150) gegenüber dem Druckraum (5d) absperrbar ist, und daß vorteilhaft eine Zuführöffnung (159) durch ein Ventilelement (160) absperrbar ist. - Einrichtung nach Anspruch 30,
dadurch gekennzeichnet, daß der Hilfskolben (150) unter dem Druck des Druckmediums im Druckraum (5d) gegen eine Gegenkraft, vorzugsweise gegen die Kraft wenigstens einer Druckfeder (16d), verschiebbar ist. - Einrichtung nach Anspruch 30 oder 31,
dadurch gekennzeichnet, daß zur Erzeugung des Drucks im Druckraum (5d) der Kolben (3d) gegen eine Gegenkraft, vorzugsweise gegen die Kraft wenigstens einer Druckfeder (4d), gegenüber dem Hilfskolben (150) verschiebbar ist. - Einrichtung nach einem der Ansprüche 30 bis 32,
dadurch gekennzeichnet, daß das Ventilelement (160) unter dem Unterdruck im Druckraum (5d) in eine die Zuführöffnung (160) freigebende Lage elastisch verformbar ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10050225 | 2000-10-11 | ||
DE10050225A DE10050225A1 (de) | 2000-10-11 | 2000-10-11 | Betätigungseinrichtung zum Festlegen einer Nockenwelle eines Antriebsmotors eines Fahrzeuges, vorzugsweise eines Kraftfahrzeuges, in einer Startposition |
Publications (3)
Publication Number | Publication Date |
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EP1197641A2 true EP1197641A2 (de) | 2002-04-17 |
EP1197641A3 EP1197641A3 (de) | 2003-01-29 |
EP1197641B1 EP1197641B1 (de) | 2005-02-09 |
Family
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EP01123536A Expired - Lifetime EP1197641B1 (de) | 2000-10-11 | 2001-09-29 | Betätigungseinrichtung zum Festlegen einer Nockenwelle eines Antriebsmotors eines Fahrzeuges in einer Startposition |
Country Status (4)
Country | Link |
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US (3) | US6739297B2 (de) |
EP (1) | EP1197641B1 (de) |
DE (2) | DE10050225A1 (de) |
ES (1) | ES2233543T3 (de) |
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DE102009054055A1 (de) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Schaltbare Vorrichtung zur Druckversorgung |
DE102009054053A1 (de) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Druckspeicher und hydraulisches System |
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Cited By (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1596039A3 (de) * | 2004-05-14 | 2007-06-20 | hofer mechatronik GmbH | Ventil, insbesondere zur Steuerung einer Nockenwellenverstelleinrichtung für Kraftfahrzeuge |
EP1596039A2 (de) * | 2004-05-14 | 2005-11-16 | hofer mechatronik GmbH | Ventil, insbesondere zur Steuerung einer Nockenwellenverstelleinrichtung für Kraftfahrzeuge |
WO2011012370A3 (de) * | 2009-07-25 | 2013-06-06 | Schaeffler Technologies Gmbh & Co. Kg | Vorrichtung zur variablen einstellung der steuerzeiten von gaswechselventilen einer brennkraftmaschine |
WO2011012370A2 (de) * | 2009-07-25 | 2011-02-03 | Schaeffler Technologies Gmbh & Co. Kg | Vorrichtung zur variablen einstellung der steuerzeiten von gaswechselventilen einer brennkraftmaschine |
DE102009054054A1 (de) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Montageanordnung und Verfahren zur Montage eines Druckspeichers für Brennkraftmaschinen |
DE102009054052A1 (de) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Schaltbare Vorrichtung zur Druckversorgung |
DE102009054051A1 (de) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Schaltbare Vorrichtung zur Druckversorgung mit passivem Zusatzdruckspeicher |
DE102009054055A1 (de) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Schaltbare Vorrichtung zur Druckversorgung |
DE102009054053A1 (de) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Druckspeicher und hydraulisches System |
DE102009054050A1 (de) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Schaltbare Vorrichtung zur Druckversorgung |
US8485152B2 (en) | 2009-11-20 | 2013-07-16 | Schaeffler Technologies AG & Co. KG | Switchable pressure supply device comprising a passive auxiliary pressure accumulator |
US8752518B2 (en) | 2009-11-20 | 2014-06-17 | Schaeffler Technologies Gmbh & Co. Kg | Switchable pressure supply device |
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DE102009054052B4 (de) | 2009-11-20 | 2018-08-23 | Schaeffler Technologies AG & Co. KG | Schaltbare Vorrichtung zur Druckversorgung |
Also Published As
Publication number | Publication date |
---|---|
ES2233543T3 (es) | 2005-06-16 |
US6968815B2 (en) | 2005-11-29 |
US6739297B2 (en) | 2004-05-25 |
DE10050225A1 (de) | 2002-04-25 |
US7107952B2 (en) | 2006-09-19 |
DE50105289D1 (de) | 2005-03-17 |
EP1197641A3 (de) | 2003-01-29 |
US20040187816A1 (en) | 2004-09-30 |
US20020088417A1 (en) | 2002-07-11 |
EP1197641B1 (de) | 2005-02-09 |
US20040187817A1 (en) | 2004-09-30 |
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