EP1197641B1 - 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
- EP1197641B1 EP1197641B1 EP01123536A EP01123536A EP1197641B1 EP 1197641 B1 EP1197641 B1 EP 1197641B1 EP 01123536 A EP01123536 A EP 01123536A EP 01123536 A EP01123536 A EP 01123536A EP 1197641 B1 EP1197641 B1 EP 1197641B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- adjusting device
- pressure
- piston
- valve
- camshaft
- 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.)
- Expired - Lifetime
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- 238000007789 sealing Methods 0.000 claims description 18
- 238000011144 upstream manufacturing Methods 0.000 claims 1
- 230000006835 compression Effects 0.000 description 18
- 238000007906 compression Methods 0.000 description 18
- 238000002485 combustion reaction Methods 0.000 description 10
- 239000007858 starting material Substances 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 239000013013 elastic material Substances 0.000 description 1
- RDYMFSUJUZBWLH-UHFFFAOYSA-N endosulfan Chemical compound C12COS(=O)OCC2C2(Cl)C(Cl)=C(Cl)C1(Cl)C2(Cl)Cl RDYMFSUJUZBWLH-UHFFFAOYSA-N 0.000 description 1
- 239000000463 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
-
- 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
-
- 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 adjusting device with an actuating device and a camshaft adjuster according to the preamble of the claim 1.
- the Camshaft assume a predetermined starting position. It happens that the engine abruptly stops in the misaligned camshaft position comes, for example, the unintentional release of the clutch increased speed at the traffic light start. Because the camshaft adjustment at increased Speed is running, the camshaft adjuster has stopped the time to get back into its starting position corresponding to the low speed. The drive motor is therefore with adjusted camshaft. This has the consequence that the drive motor does not start or only with difficulty.
- the invention is based on the object, the generic adjustment form so that the camshaft reliably in their starting position arrives.
- the camshaft is through a forced control adjusted to their starting position and held there. Thereby It is ensured that the camshaft when switching off the engine Reliably takes her starting position.
- the drive motor can be around it restart easily.
- the forced control is also achieved that the camshaft is also required in their to start the engine Start position, for example, by stalling the engine at different speeds assumes a different position. Is the starter in started in such a case, is achieved by the forced control that the camshaft reaches the start position after a short time.
- the Pressure medium is from the additional storage as additional volume for adjustment fed to the piston of the rotary valve so that it quickly into the required Starting position is adjusted.
- the additional storage is to the atmosphere open, so that the adjusting device according to the invention a simple Structure has and can be produced inexpensively.
- the actuating device has a piston rod 1, on which a slider 2 sits.
- the piston rod 1 is at its in Fig. 1st provided on the left end with a piston 3, to which the one end a compression spring 4 is supported. It lies in a pressure chamber 5, in a hydraulic line 6 opens. It connects the pressure chamber 5 with a buffer 7, which via an overflow line 8 with a tank 9 is connected.
- In the hydraulic line 6 is located in Direction to the pressure chamber 5 opening check valve 10th
- the slide 2 is provided on the circumference with three annular grooves 11 to 13, which are separated by ring lands 14, 15.
- the slider 2 is under the force of at least one compression spring 16 in a 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 replaced by a plunger 20 against the force of Compressed spring 4 shifted.
- the plunger 20 is part of a solenoid valve 21, which in addition to the piston rod 1 and the slide 2 has. Of the Plunger 20 is in a known manner by a (not shown) Anchor shifted when the solenoid valve 21 is energized.
- the solenoid valve 21 has two tank connections T which are connected to a common Tank line 22 are connected, in the buffer 7 opens. In the tank line 22 sits against the buffer 7 opening check valve 23.
- the hydraulic medium is from the tank 9 via a pump 25 in the pressure line 24th promoted, in a closing against the tank 9 check valve 26 is sitting.
- transverse line 27 From the pressure line 24 opens in the area in front of the pressure connection P a transverse line 27 from which the pressure chamber 5 with the pressure line 24 connects. In the transverse line 27 sits in the direction of the Pressure line 24 opening check valve 28.
- the solenoid valve 21 is also provided with two working ports A, B Mistake.
- the working port A serves a crankshaft of a Internal combustion engine for the starting process in a start position too bring.
- the working port B is for the adjustment of the camshaft provided with the internal combustion engine.
- the piston 3 of the piston rod 1 is under the force of the compression spring 4 and under the located in the pressure chamber 5 hydraulic medium the housing wall 19 at.
- the slider 2 is under the force of Compression spring 16 on a housing-side stop 29 at.
- In this Position is the middle annular groove 12 of the slider 2 via the pressure connection P with the annular groove 11 and thus with the working port A. connected.
- the working connection B is through the annular web 15 of Pressure port P separated and connected to the tank port T.
- the buffer 7 forms an additional Hydraulic medium volume, whereby the piston 3 very can be quickly adjusted to the starting position shown in FIG. 1.
- the buffer 7 is atmospherically open.
- About the additional Hydraulic fluid is the camshaft adjuster 32 at Starting process so much hydraulic fluid supplied to the camshaft adjusted to the starting position with the first turns and in this location can be locked if necessary.
- FIG. 2 shows an actuating device with which the camshaft of the camshaft adjuster 32 hydraulically adjusted to a starting position.
- the phaser 32 is in Figs. 2 to 9 shown only schematically.
- the solenoid valve 21 is not energized in the position shown in FIG. 2, so that the hydraulic medium under pressure via the pressure line 24th to the working connection A of a camshaft adjuster 32 (FIGS 12). He has pressure chambers 97 (Fig. 12), in which the hydraulic medium reaches and the camshaft 31 in later to be described Mode in the start position (Fig. 12) adjusted. That in the unimpaired Pressure chambers 85 located hydraulic medium is over the tank line 22 and the check valve 23 in the buffer 7 displaced.
- the solenoid valve 21 switched. As a result, the pressurized hydraulic medium passes into the pressure chambers 85 ( Figures 11 and 12) and rotate the camshaft 31 in the opposite direction. That in the pressure chambers 97 located hydraulic medium is via the terminal 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 variety of layers depending on the necessary adjustment can be turned.
- FIG. 3 sits in the intermediate line 37 an electromagnetic pump 39. It has an armature 40, the is designed as a piston rod and at the free end a piston 41st wearing. It separates two pressure chambers 42, 43 in a cylinder 44 from each other.
- the armature 40 is located in its outside of the cylinder 44 Area surrounded by a coil 45.
- the intermediate line 37 extends over the pressure chamber 43 in the buffer 7.
- the check valve 38 which locks in the direction of the cache 7. Otherwise it is the actuating device of the same design as the embodiment according to FIG. 2.
- the hydraulic pressure whereby the camshaft 31st rotated so far according to the previous embodiment is that it assumes its starting position (Fig. 12). That in the pressure chambers 85 (FIG. 11) is hydraulic medium via the solenoid valve 21 and the tank line 22 to the latch 7 returned.
- the coil 45 of the electromagnetic pump 39 is energized, so that the armature 40 is moved in Fig. 3 to the right.
- the pump 39 presses the hydraulic medium from the buffer 7 on the intermediate line and a sitting in her Check valve 46 in the pressure line 24. Due to the temporary storage 7 is thus according to the previous embodiments ensures that through the addition of the pressure line 24 supplied hydraulic medium, the camshaft 31 quickly in the stop position described is rotated.
- the intermediate line 37 opens according to the embodiment 2 in the area between the check valve 26 and the Solenoid valve 21 in the pressure line 24th
- FIG. 4 branches from the pressure line 24th in the area between the pump 25 and the check valve 26 a Transverse line 47 from, in the direction of the pressure line 24th locking check valve 48 is seated.
- the transverse line 47 leads to a Accumulator 49, stored in the hydraulic medium under pressure is.
- the intermediate line 37 from where in the direction of the transverse line 47 closing Check valve 46 is located and the electromagnetic pump 39th leads. If the coil 45 of the pump 39 is not energized, the armature 40 takes the position shown in Fig. 4, in which the piston 41 of the armature 40, the intermediate line 37 blocks.
- In the pressure room 43 of the Pump 39 opens an intermediate line 50, in the direction of the pressure chamber 43 locking check valve 51 is seated and in the Region between the check valve 26 and the solenoid valve 21st opens into the pressure line 24.
- the hydraulic medium located in the pressure accumulator 49 can thus under pressure via the check valve 46 in the Pressure chamber 43 of the pump 39 reach. From here comes the hydraulic medium via the check valve 51 in the pressure line 24th Due to this additional hydraulic volume, the camshaft 31st quickly turned to its starting position.
- a further solenoid valve 52 is provided with the inflow of the hydraulic medium from the pressure accumulator 49 in the Pressure line 24 is controlled. Should the camshaft in the start position be secured, the solenoid valve 21 is switched so that the pressure chambers 97 of the camshaft adjuster 32 with the pressure line 24 are connected. In addition, the solenoid valve 52 is off Switched the position shown in Fig. 5, so that the intermediate line 37 is connected to the intermediate line 50. Then that can located in the pressure accumulator 49, pressurized hydraulic medium additionally be conveyed in the pressure line 24, so that the Camshaft 31 is rapidly rotated to its stop position.
- the actuator of FIG. 6 is formed similar to the Embodiment of Fig. 2. It has in addition to the tank 9 the Latch 7, which via the overflow line 8 with the tank. 9 connected is.
- the buffer 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 hydraulic medium directed into the pressure chambers 97 of the camshaft adjuster 32 so that the camshaft 31 is rotated to its stop position.
- the intermediate line 37 sits in the direction of the camshaft adjuster 32 opening check valve 53.
- the camshaft 31 is characterized in fast the starting position turned. That in the pressure chambers 85 of the camshaft adjuster 32 located hydraulic medium is via the tank line 22 back to the buffer 7 out.
- the solenoid valve 21 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 Pressure chambers 97 located hydraulic medium is not on the intermediate line 37, but only via the tank line 22 in the buffer 7 is displaced.
- the embodiment of FIG. 7 largely corresponds to the embodiment as shown in FIG. 3.
- the intermediate line 37 opens in 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 is turned on, so that the piston 41 in the position is pushed as shown in FIG. 7 and hydraulic medium from the pressure chamber 43 via the intermediate line 37 in the pressure line 24 as an additional Hydraulic volume promotes. Through this additional volume the rotational movement of the camshaft 31 is in the starting position accelerated.
- the solenoid valve 21 switched from the position shown in FIG. 7, so that the pressure chambers 97 of the camshaft adjuster 32 with the tank line 22 and the pressure chambers 85 of the camshaft adjuster 32 with the pressure line 24 are connected.
- the hydraulic medium is thus at Turning back the camshaft 31 from the pressure chambers 97 via the Tank line 22 is returned to the buffer 7.
- the actuator of FIG. 8 largely corresponds to Embodiment according to FIG. 4. The only difference is that that the intermediate line 50 in the area between the solenoid valve 21 and the camshaft 31 opens into the pressure line 24.
- FIG. 9 differs from the embodiment as shown in FIG. 5 only in that the intermediate line 50 in the region between the solenoid valve 21 and the camshaft 31 opens into the pressure line 24.
- FIGS. 8 and 9 same as the embodiments of FIGS. 4 and 5.
- FIGS. 10 to 12 show in detail the camshaft adjuster 32, with which the camshaft 31 can be rotated.
- a rotary valve 54 On the camshaft 31 rotatably seated a rotary valve 54, which is in a cylindrical Housing 55 is limited rotation.
- the housing 55 indicates its inner wall radially inwardly projecting webs 56 to 60, which are arranged distributed uniformly over the circumference and end faces 61 to 65, with which they flat on the cylindrical outer shell 66 of the rotary valve 54 abut.
- the rotary valve 54 has radially projecting beyond the outer jacket 66 Arms 67 to 71, which protrude between the webs 56 to 60 and with their curved end faces 72 to 76 flat on the cylindrical inside 77 of the housing 55 abut.
- the measured in the circumferential direction Width of the arms 67 to 71 is smaller than the distance between neighboring bridges 56 to 60.
- the housing 55 has two mutually parallel, annular Cover 78, 79 (Fig. 10), between which the rotary valve 54 is located. At the outer edge, the two covers 78, 79 through a ring 80th connected to each other, the cylindrical inner side 77 of the housing 55 has. The two covers 78, 79 are located on the two Side surfaces of the rotary valve 54 at.
- the rotary valve 54 is seated on a threaded bolt 81, with the Rotary valve 54 with one end 82 of the camshaft 31 attached 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 the radially extending, the rotary valve 54 passing through holes 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 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 shows the rotary valve 54 in the one stop position in which his arms 67 to 71 abut the left in Fig. 11 side walls of the webs 56 to 60.
- the webs 56 to 60 are on both side walls with in Provided circumferentially extending projections 86 and 87, where the arms 67 to 71 of the rotary valve 54 abut.
- the axial bore 83 of the manifold 82 is via a transverse bore 88 connected to an annular groove 89 in the outer shell of the camshaft end 82 provided and by a ring 90 radially to outside is limited.
- annular groove 89 opens a hole 91, via which the hydraulic medium from the tank 9 and from the buffer 7 is supplied.
- the camshaft end 82 is at its outer circumferential surface with a further annular groove 92 provided (FIG. 10) through the ring 90th is closed radially outward 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.
- the annular groove 95 open the rotary valve 54 radially passing through Holes 96, in the thinner wall portion of the rotary valve 54th are provided and open into the pressure chambers 97, the between the webs 56 to 60 of the housing 55 and the arms 67 to 71 of Rotary valve 54 are.
- the pressure chambers 85 and 97 are through the Arms 67 to 71 of the rotary valve 54 separated from each other.
- solenoid valve 21 By switching the (not shown) solenoid valve 21 is the hydraulic medium in the described with reference to FIGS. 1 to 9 Way over the annular groove 89, the transverse bore 88, the axial bore 83 and the radial bores 84 passed into the pressure chambers 85.
- the rotary valve 54 in the illustration of FIG. 11th and 12 in a clockwise direction relative to the housing 55 in the direction of the opposite webs or projections 87 are rotated. Since the Rotary valve 54 rotatably connected to the camshaft 31 is turned them to the appropriate extent.
- the in the pressure chambers 97th located hydraulic medium is through the radial bores 96, the Ring groove 95, the axial bore 94, the annular groove 92 and the bore 93rd back to the tank 9 or displaced to the buffer 7.
- Fig. 13 shows a solenoid valve 21 a, the plunger 20 a at a Pressure piston 98 is applied.
- a dome-shaped head 99 is the Pressure piston 98 on a resilient plate 100, which in the embodiment made of rubber-elastic material or rubber can exist.
- the plate 100 is at its periphery in the housing 18a clamped.
- a bush 101 is inserted into the housing 18a, secured with a locking ring 102 in the housing 18a is.
- the plate 100 is between that facing away from the retaining ring 102 End of the sleeve 101 and a radial shoulder surface 103rd clamped, which protrudes from the inner wall of the housing 18 a.
- the Bushing 101 has a bottom 104 which is at least one bore 105, in the embodiment of two holes 105, axially interspersed is.
- the holes 105 are at their from the locking ring 102nd opposite end closed by a valve plate 106, which with a screw 107 fixed to the bottom 104 of the sleeve 101 is.
- the valve plate 106 is elastic at least in the edge region compliantly educated.
- the bores 105 communicate with the hydraulic line 6 (FIG. 1), about the hydraulic medium from the buffer is supplied. Between the plate 100 and the valve plate 106 is located the pressure chamber 5a.
- the socket 101 and the wall of the housing 18a is provided with transverse bores 108, 109, the aligned with each other.
- the transverse bores 108 of the bushing 101 are closed by a ring 110 which is elastically expandable and in an annular groove 111 housed in the outer wall of the sleeve 101 is.
- the solenoid valve 21a operates basically in the same way as it has been described with reference to the embodiment of FIG. 1. If the plunger 20a of the solenoid valve 21a by turning on the Solenoid valve in Fig. 13 shifted to the left, via the pressure piston 98, the plate 100 elastically toward the valve plate 106th deformed. As a result, the hydraulic medium in the pressure chamber 5a put under pressure. By this pressure, the ring 110th elastically expanded, so that the hydraulic medium over the now open Transverse holes 108 from the pressure chamber 5a through the transverse bores 109 can flow to the respective work connection. By the pressure in the pressure chamber 5a, the valve plate 106 is firmly in their in 13 shown closed position, so that the hydraulic medium can not get into the holes 105. This will be the Camshaft 31 is rotated in the manner described in the start position.
- the solenoid valve 21b the plunger 20b, which acts on the piston 3b. He is in an axial bore 112 of the valve housing 18b out.
- the pressure chamber 5b is by the piston 3b and a bottom 113 of the valve housing 3b axially limited.
- the transverse bore 115 is connected to the hydraulic line 6 (FIG. 1), about which the hydraulic medium from the buffer 7 is conveyed into the pressure chamber 5b.
- the pressure port P (FIG. 1) is connected to the cross hole 114.
- a socket 116, 117 In the two transverse bores 114, 115 is in each case a socket 116, 117.
- the bottom 118, 119 of the bushes 116, 117 is each with a central passage opening 120, 121 provided.
- the passage opening 120 of the sleeve 116 faces the pressure chamber 5b while the through hole 121 of the sleeve 117 from the pressure chamber 5b turned away.
- On the floor 118, 119 of the bushes 116, 117 On the floor 118, 119 of the bushes 116, 117 is located in each case an elastically deformable valve plate 122, 123, which in suitably secured to the floor and the passage opening 120, 121 closes in the closed position.
- the star-shaped arms 126, 127 has, between which the hydraulic medium in the pressure chamber 5b and out can flow to the pressure chamber 5b.
- the arms 126, 127 are radial from the upper end of a central body 128, 129 from, with Distance from the bushing 116, 117 is surrounded.
- the arms 126, 127 the flow distributor 124, 125 sit on a radial shoulder surface 130, 131 on the inside of the bushes 116, 117 and are attached to it in an appropriate manner. It is also possible the arms 126, 127 in the sockets 116, 117 press.
- the passage opening 121 is connected to the hydraulic line 6 (FIG. 1), over which the hydraulic medium in the described Way can get into the pressure chamber 5b. This raises the Valve plate 123 from the bottom 119 of the bush 117, so that the hydraulic medium between the arms 127 of the flow distributor 125 can get into the pressure chamber 5b.
- the solenoid valve 21 c of FIG. 15 has the plunger 20 c, the on the Piston 3c acts. It is over part of its length on the inner wall a bushing 132, which in the axial bore 112 c of Valve housing 18c is inserted.
- the piston 3c is at its from Plunger 20c facing away from end face with a central recess 133rd provided, in which engages the one end of a compression spring 4c. Your other End sits in a central recess 134 a cup-shaped Receiving 135, which with an end-side flange 136 between the Bottom 113c of the valve housing 18c and one at the socket 132nd adjacent ring 141 is clamped.
- the sleeve 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 in a manner to be described in the pressure chamber 5c flow can.
- Another annulus 138 is between the sleeve 132 and formed a part of the length of the piston 3c.
- annular spaces 137 and 138 each open over the circumference of the Valve housing 18c arranged distributed through holes 139th and 140, which the valve housing 18c and the sleeve 132 radially push through.
- the socket 132 two rings 141, 142 are inserted, with which sealing rings 143 to 145 are secured, in the inner wall the sleeve 132 are arranged and fixed in it.
- the through holes 139, 140 are the two rings 141, 142 provided with appropriate holes.
- the sealing ring 143 lies with Distance from the flange 136 of the receptacle 135 and seals the annulus 137 against the pressure chamber 5c from.
- the annular space 138 is separated by the two at an axial distance lying sealing rings 144 and 145 limited, of which the Sealing ring 144 seals the annular space 138 against the pressure chamber 5c.
- the sealing lips of the two sealing rings 144, 145 are inclined in the direction directed towards each other.
- Fig. 16 shows a solenoid valve 21d, whose plunger 20d on the piston 3d is applied. It is axial over part of its length in sleeve 132d guided. It has one end facing the plunger 20d radially outwardly directed flange 146, with which they at a radial Shoulder surface 147 on the inside of the valve housing 18d is applied.
- the solenoid valve 21d has a central body 148, the according to the previous embodiments axially over the housing part 149 of the magnetic part of the solenoid valve 21d axially protrudes.
- the protruding end of the main body 148 is mushroom-shaped educated. On this protruding end is the valve body 18d placed form-fitting over a flange.
- the flange 146 of the sleeve 132 d is between the shoulder surface 147 and the End face of the protruding end of the base 148 clamped.
- auxiliary piston 150 On the piston 3d sits an auxiliary piston 150, the on of the socket 146 facing away from a radially outwardly directed flange 151 has. With him the auxiliary piston 150 is not energized Solenoid valve 21d at a radially inwardly extending shoulder surface 152, on the inner wall of the axial bore 112d of the Valve housing 18d is provided under the force of the compression spring 16d on. It also rests against the face of sleeve 132d from.
- the piston 3d is under the force of the compression spring 4d, with a End to a flow body 153 and with its other end an inner radial shoulder surface 154 supported in the piston 3d is.
- the flow body 153 is 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 from each other 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 main body 155 is spaced from the inner wall of the valve body Surrounding 18d, creating an annulus 158 between the body 155 and the inner wall of the valve housing 18d is formed.
- annular space 158 opens centrally a hole 159 in the ground 113d of the valve housing 18d.
- the bore 159 is through the valve plate 160 closed, which consists of elastically yielding material and is fixed on the floor 113d so as to be released the bore 159 can bend away elastically.
- the auxiliary piston 150 defines radially inwardly an annular space 161, the radially outwardly through the wall of the valve housing 18d is limited. In this annular space 161 open the wall of the valve housing 18d radially passing through holes 162nd
- the solenoid valve 21d If the solenoid valve 21d is not energized, the auxiliary piston 150 is under the force of the compression spring 16d on the shoulder surface 152 sealing at. As a result, the annular space 161 is separated from the pressure chamber 5d, the between the piston 3d and the flow body 153 is located. The Valve plate 160 closes the axial bore 159. Will the solenoid valve Energized 21d, the plunger 20d pushes the piston against 3d the force of the compression spring 4d, whereby the located in the pressure chamber 5d Hydraulic medium is pressurized. This pressure is bigger as exerted by the compression spring 16d on the auxiliary piston 150 Counterforce, so that the auxiliary piston 150 by the hydraulic medium is pushed back.
- the described solenoid valves 21a to 21d shown in FIGS. 13 to 16 can be used in the adjusting devices according to FIGS. 1 to 9 become.
Description
- Fig. 1
- eine erfindungsgemäße Verstelleinrichtung,
- Fig. 2 bis Fig. 9
- jeweils Hydraulikpläne von erfindungsgemäßen Verstelleinrichtungen,
- Fig. 10
- einen Axialschnitt durch einen Nockenwellenversteller der erfindungsgemäßen Nockenwellenverstelleinrichtung,
- Fig. 11
- einen Schnitt längs der Linie A-A in Fig. 10,
- Fig. 12
- einen Schnitt längs der Linie B-Bi in Fig. 10,
- Fig. 13 bis Fig. 16
- verschiedene Ausführungsformen von Magnetventilen der erfindungsgemäßen Verstelleinrichtung.
Claims (37)
- Verstelleinrichtung mit einer Betätigungseinrichtung und einem Nokkenwellenversteller (32), der einen in einem Gehäuse (55) befindlichen Drehschieber (54) aufweist, der drehfest mit einer Nockenwelle (31) eines Antriebsmotors eines Fahrzeuges, verbunden ist und wenigstens einen Kolben (67 bis 71) aufweist, der beidseitig mit einem Druckmedium beaufschlagbar ist, das aus einem Tank (9) mit der Betätigungseinrichtung zuführbar ist, mit der die Nockenwelle (31) durch eine Zwangsteuerung in eine Startposition verstellbar ist, dadurch gekennzeichnet, daß das Druckmedium in einem Zusatzspeicher (7, 49) als Zusatzvolumen zur Verstellung des Kolbens (67 bis 71) zuführbar ist.
- Verstelleinrichtung nach Anspruch 1,
dadurch gekennzeichnet, daß die Betätigungseinrichtung zur Verstellung der Nockenwelle (31) ein Magnetventil (21, 21a bis 21d) aufweist, mit dem der Zufluß des Druckmediums steuerbar ist. - Verstelleinrichtung nach Anspruch 2,
dadurch gekennzeichnet, daß der Tank (9) über eine Druckleitung (24) mit einem Druckanschluß (P) des Magnetventiles (21, 21a bis 21d) verbunden ist. - Verstelleinrichtung nach einem der Ansprüche 1 bis 3,
dadurch gekennzeichnet, daß der Zusatzspeicher (7) über wenigstens eine Überlaufleitung (8) mit dem Tank (9) des Druckmediums verbunden ist. - Verstelleinrichtung nach einem der Ansprüche 1 bis 4,
dadurch gekennzeichnet, daß dem Zusatzspeicher (7, 49) wenigstens eine Pumpe (39) nachgeschaltet ist, die einen Kolben (41) aufweist, mit dem das Zusatzvolumen dem Druckmedium zuführbar ist. - Verstelleinrichtung nach Anspruch 5,
dadurch gekennzeichnet, daß der Kolben (41) der Pumpe (39) eine Zuleitung (37) für das Zusatzvolumen in einer Ausgangslage schließt. - Verstelleinrichtung nach einem der Ansprüche 2 bis 6,
dadurch gekennzeichnet, daß das Druckmedium aus dem Nockenwellenversteller (32) nach dem Starten des Antriebsmotors und Umschalten des Magnetventiles (21) in den Zusatzspeicher (7) zurückführbar ist. - Verstelleinrichtung, insbesondere nach einem der Ansprüche 1 bis 7,
dadurch gekennzeichnet, daß die Verstelleinrichtung einen Schieber (2) aufweist, der auf einer Kolbenstange (1) angeordnet ist. - Verstelleinrichtung nach Anspruch 8,
dadurch gekennzeichnet, daß die Kolbenstange (1) relativ zum Schieber (2) verschiebbar ist, der durch einen Anschlag (30) auf der Kolbenstange (1) gegen eine Gegenkraft verschiebbar ist. - Verstelleinrichtung nach Anspruch 8 oder 9,
dadurch gekennzeichnet, daß der Schieber (2) und die Kolbenstange (1) Teil des Magnetventiles (21) sind. - Verstelleinrichtung nach einem der Ansprüche 8 bis 10,
dadurch gekennzeichnet, daß die Kolbenstange (1) einen Kolben (3) trägt, der in einer Ausgangsstellung unter Kraft an einem gehäuseseitigen Anschlag (19) des Magnetventiles (21) anliegt. - Verstelleinrichtung nach einem der Ansprüche 8 bis 11,
dadurch gekennzeichnet, daß die Kolbenstange (1) einen vorgeschalteten Druckraum (5) begrenzt, der an den Zusatzspeicher (7) angeschlossen ist. - Verstelleinrichtung nach Anspruch 12,
dadurch gekennzeichnet, daß der Druckraum (5) über eine Leitung (27) mit der Druckleitung (24) verbunden ist. - Verstelleinrichtung nach Anspruch 13,
dadurch gekennzeichnet, daß in der Leitung (27) ein in Richtung auf die Druckleitung (24) öffnendes Rückschlagventil (28) sitzt. - Verstelleinrichtung nach einem der Ansprüche 1 bis 14,
dadurch gekennzeichnet, daß der Drehschieber (54) im Gehäuse (55) begrenzt drehbar ist und als Kolben mehrere radial abstehende Arme (67 bis 71) aufweist. - Verstelleinrichtung nach Anspruch 15,
dadurch gekennzeichnet, daß das Gehäuse (55) mehrere radial nach innen ragende Stege (56 bis 60) aufweist, zwischen welche die Arme (67 bis 71) des Drehschiebers (54) eingreifen. - Verstelleinrichtung nach einem der Ansprüche 1 bis 16,
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. - Verstelleinrichtung nach einem der Ansprüche 1 bis 17,
dadurch gekennzeichnet, daß das Druckmedium axial über wenigstens eine Bohrung in der Nockenwelle (31) dem Nockenwellenversteller (32) zuführbar ist. - Verstelleinrichtung nach einem der Ansprüche 16 bis 18,
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. - Verstelleinrichtung nach einem der Ansprüche 1 bis 19,
dadurch gekennzeichnet, daß der Drehschieber (54) axial gesichert zwischen zwei miteinander verbundenen Deckeln (78, 79) des Gehäuses (55) liegt. - Verstelleinrichtung, insbesondere nach einem der Ansprüche 1 bis 20,
dadurch gekennzeichnet, daß sie ein Magnetventil (21, 21a bis 21d) aufweist, dessen Ventilteil als Pumpe ausgebildet ist. - Verstelleinrichtung nach Anspruch 21,
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. - Verstelleinrichtung nach Anspruch 22,
dadurch gekennzeichnet, daß das Druckmedium in den Druckraum (5, 5a bis 5d) mittels Unterdruck förderbar ist. - Verstelleinrichtung nach einem der Ansprüche 21 bis 23,
dadurch gekennzeichnet, daß das Magnetventil (21a) einen Kolben (98) aufweist, mit dem bei Bestromen des Magnetventils wenigstens ein den Druckraum (5a) begrenzendes, durch den Kolben (98) elastisch verformbares Druckelement (100) zur Erzeugung des Druckes im Druckraum (5a) verstellbar ist. - Verstelleinrichtung nach Anspruch 24,
dadurch gekennzeichnet, daß in den Druckraum (5a) wenigstens eine Bohrung (105) mündet, über die das Druckmedium zuführbar ist und die durch ein unter dem Unterdruck von der Bohrung (105) abhebendes Ventilelement (106) verschließbar ist. - Verstelleinrichtung nach Anspruch 25,
dadurch gekennzeichnet, daß das Ventilelement (106) zur Freigabe der Bohrung (105) elastisch verformbar ist. - Verstelleinrichtung nach einem der Ansprüche 24 bis 26,
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. - Verstelleinrichtung nach Anspruch 27,
dadurch gekennzeichnet, daß die 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. - Verstelleinrichtung nach Anspruch 27 oder 28,
dadurch gekennzeichnet, daß die Ventilelemente (122, 123) elastisch verformbar sind. - Verstelleinrichtung nach einem der Ansprüche 21 bis 23,
dadurch gekennzeichnet, daß der Druckraum (5c) durch jeweils wenigstens eine Dichtung (143, 144) gegen wenigstens eine Zuführöffnung (139) und wenigstens einen Arbeitsanschluß (140) abgedichtet ist. - Verstelleinrichtung nach Anspruch 30,
dadurch gekennzeichnet, daß die dem Arbeitsanschluß (140) zugeordnete Dichtung (144) am Kolben (3c) dichtend anliegt. - Verstelleinrichtung nach Anspruch 30 oder 31,
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. - Verstelleinrichtung nach einem der Ansprüche 21 bis 23,
dadurch gekennzeichnet, daß der Arbeitsanschluß (162) durch einen auf dem Kolben (3d) verschiebbar gelagerten Hilfskolben (150) gegenüber dem Druckraum (5d) absperrbar ist. - Verstelleinrichtung nach Anspruch 33,
dadurch gekennzeichnet, daß eine Zuführöffnung (159) durch ein Ventilelement (160) absperrbar ist. - Verstelleinrichtung nach Anspruch 33 oder 34,
dadurch gekennzeichnet, daß der Hilfskolben (150) unter dem Druck des Druckmediums im Druckraum (5d) gegen eine Gegenkraft verschiebbar ist. - Verstelleinrichtung nach einem der Ansprüche 33 bis 35,
dadurch gekennzeichnet, daß zur Erzeugung des Drucks im Druckraum (5d) der Kolben (3d) gegen eine Gegenkraft gegenüber dem Hilfskolben (150) verschiebbar ist. - Verstelleinrichtung nach einem der Ansprüche 34 bis 36,
dadurch gekennzeichnet, daß das Ventilelement (160) unter dem Unterdruck im Druckraum (5d) in eine die Zuführöffnung (159) freigebende Lage elastisch verformbar ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10050225A DE10050225A1 (de) | 2000-10-11 | 2000-10-11 | Betätigungseinrichtung zum Festlegen einer Nockenwelle eines Antriebsmotors eines Fahrzeuges, vorzugsweise eines Kraftfahrzeuges, in einer Startposition |
DE10050225 | 2000-10-11 |
Publications (3)
Publication Number | Publication Date |
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EP1197641A2 EP1197641A2 (de) | 2002-04-17 |
EP1197641A3 EP1197641A3 (de) | 2003-01-29 |
EP1197641B1 true EP1197641B1 (de) | 2005-02-09 |
Family
ID=7659325
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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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-
2000
- 2000-10-11 DE DE10050225A patent/DE10050225A1/de not_active Withdrawn
-
2001
- 2001-09-29 ES ES01123536T patent/ES2233543T3/es not_active Expired - Lifetime
- 2001-09-29 EP EP01123536A patent/EP1197641B1/de not_active Expired - Lifetime
- 2001-09-29 DE DE50105289T patent/DE50105289D1/de not_active Expired - Fee Related
- 2001-10-11 US US09/975,301 patent/US6739297B2/en not_active Expired - Fee Related
-
2004
- 2004-04-13 US US10/709,092 patent/US7107952B2/en not_active Expired - Fee Related
- 2004-04-13 US US10/709,093 patent/US6968815B2/en not_active Expired - Fee Related
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8453616B2 (en) | 2009-10-27 | 2013-06-04 | Hilite Germany Gmbh | Vane-type motor cam phaser with a friction disc and mounting method |
US8794201B2 (en) | 2009-10-27 | 2014-08-05 | Hilite Germany Gmbh | Vane-type motor cam phaser with a friction disc and method for mounting a friction disc on a rotor |
US8662040B2 (en) | 2010-04-10 | 2014-03-04 | Hilite Germany Gmbh | Oscillating-motor camshaft adjuster having a hydraulic valve |
US8505582B2 (en) | 2010-05-03 | 2013-08-13 | Hilite Germany Gmbh | Hydraulic valve |
US8752514B2 (en) | 2010-12-20 | 2014-06-17 | Hilite Germany Gmbh | Hydraulic valve for an oscillating motor adjuster |
Also Published As
Publication number | Publication date |
---|---|
ES2233543T3 (es) | 2005-06-16 |
DE50105289D1 (de) | 2005-03-17 |
DE10050225A1 (de) | 2002-04-25 |
US6739297B2 (en) | 2004-05-25 |
US6968815B2 (en) | 2005-11-29 |
US20040187817A1 (en) | 2004-09-30 |
EP1197641A3 (de) | 2003-01-29 |
US7107952B2 (en) | 2006-09-19 |
US20020088417A1 (en) | 2002-07-11 |
US20040187816A1 (en) | 2004-09-30 |
EP1197641A2 (de) | 2002-04-17 |
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