EP0163046B1 - Vorrichtung zur Winkelverstellung einer Welle, insbesondere Nockenwelle, gegenüber einem Antriebsrad - Google Patents

Vorrichtung zur Winkelverstellung einer Welle, insbesondere Nockenwelle, gegenüber einem Antriebsrad Download PDF

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Publication number
EP0163046B1
EP0163046B1 EP85103624A EP85103624A EP0163046B1 EP 0163046 B1 EP0163046 B1 EP 0163046B1 EP 85103624 A EP85103624 A EP 85103624A EP 85103624 A EP85103624 A EP 85103624A EP 0163046 B1 EP0163046 B1 EP 0163046B1
Authority
EP
European Patent Office
Prior art keywords
shaft
driving wheel
sensors
voltage
pulse generators
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
Application number
EP85103624A
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German (de)
English (en)
French (fr)
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EP0163046A1 (de
Inventor
Karl Heinz Bruss
Hans Baumgartner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Pierburg GmbH
Original Assignee
Pierburg GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Pierburg GmbH filed Critical Pierburg GmbH
Publication of EP0163046A1 publication Critical patent/EP0163046A1/de
Application granted granted Critical
Publication of EP0163046B1 publication Critical patent/EP0163046B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34403—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft

Definitions

  • the invention relates to a device according to the preamble of patent claim 1
  • a speed-dependent and load-dependent angle adjustment for controlling an internal combustion engine is to be achieved, a reference angle position and an angular rotation of the engine crankshaft, which is connected to the drive wheel, to be determined via pulse generators and sensors and to be processed into a control signal.
  • This control signal is applied to a setting device that can be driven by several drive motors and the position of which is indicated by a multi-turn potentiometer as the actual value signal.
  • This device is very complex and complicated and requires the provision of a considerable adjustment performance.
  • the actual value acquisition also appears to be too imprecise, since the actual value is not displayed directly by the camshaft.
  • a further device for changing the valve timing in which the camshaft is automatically reset at low engine outputs and is advanced at higher outputs.
  • a coupling device has two pistons pressurized with engine oil in cylindrical bores which, acting in the same direction, are intended to effect an angular adjustment.
  • For the resetting of this adjustment apart from the resetting made possible by oil leakage between the pistons and cylinders, no means are indicated, i. H. active adjustment is only possible in one direction.
  • Fig. 7 has a camshaft with a sleeve which can be adjusted in the axial direction by means of double-acting hydraulic cylinders and on which a gearwheel is rotatably mounted, but is positively coupled to the camshaft in the circumferential direction.
  • the thus axially displaceable gearwheel engages in a helical toothed off-axis drive wheel, with teeth sliding as sliding blocks in oblique tooth gaps and an angular adjustment acting between the drive and gearwheels.
  • the object is therefore not suitable for a drive by chains, toothed belts or gears with straight teeth.
  • the object of the invention is therefore to design a device of the type mentioned such that active adjustment in opposite directions is possible in the generic object, the mechanical outlay being kept within limits.
  • a detection or control of the angle adjustment should be made possible with high accuracy.
  • a versatile device for controlling a coupling device which is mechanically and hydraulically very simple.
  • Precise adjustment angle detection has become possible by means of pulse generators arranged directly on the coupling members shaft and drive wheel.
  • the digital recording of the reference or reference signals characterizing the angle adjustment and the counted actual value signals provides a link to a stored map control system without analog / digital conversion.
  • the angle can be adjusted in any direction without having to provide a large adjustment performance.
  • Fig. 1 shows the device according to the invention consisting of a bearing block 1 with two bearing points 2, 3, in which a shaft 6 constructed from two parts 4, 5 is inserted, a centering pin 7 of the shaft part 4 simultaneously having a bearing pin 8 of a toothing 9 Drive wheel 10 forms.
  • the shaft part 4 has two circumferential oil grooves 11, 12 in the area of the bearing point 2, which are aligned with two oil bores 13, 14 of the bearing block 1 opening out in the bearing point 2.
  • Each of these bores 13, 14 is connected via a throttle 15 to a pressure line 16 of an oil pump 17 and has a relief bore 18, 19 which is controlled by an electrically operable valve 20, 21 and opens into an oil reservoir 22.
  • a bore 23, 24 extends from the oil grooves 11, 12 to a respective cylinder 26, 27, as can be seen in FIG. 2, having a piston 25, the two cylinders 26, 27 being arranged symmetrically.
  • a slide 29 Arranged in a transverse bore 28 connecting the bores 23, 24 is a slide 29 which is spring-loaded on both sides and which has the cross sections of the bores 23, 24 leading to the cylinders 26, 27 closes when pressure is equal in the bores 23, 24, the end face: 30, 31 of the slide 29 being acted upon by the pressure prevailing there via a line 32 from each of the bores 23, 24.
  • the shaft 6 and the drive wheel 10 have pulse generators 36, 38, which are each arranged on the outer circumference and are intended to act on sensors 37, 39 fastened to the bearing block 1.
  • FIG. 3 shows a partial view of an embodiment variant of the device shown in FIG. 1, which differs from FIG. 1.
  • the components which have not been dealt with in more detail and which have the same numbers are identical to those of FIGS. 1 and 2.
  • a shaft part 40 is shown, which corresponds to the shaft part 4 of FIG. 1 and forms with the shaft part 5, not shown, the shaft 6, which is inserted into the bearing block 3, not shown, and a 41 shown bearing block.
  • the shaft part 40 has a bore 42 arranged in the center in the axial direction with a multi-offset bushing 43, in which a slide 44 is arranged axially displaceably, which is counteracted by an actuator 46 fastened in a rotationally fixed manner to a cover hood 45 via a rod 47 inserted into the slide 44 the force of two springs 48, 49 can be adjusted so that three defined slide positions can be reached, which are shown as the central position in FIG. 3 and opposite end positions in FIGS. 4 and 5.
  • Slider 44 controls control bores 54, 55 arranged in the bush 43 with cylinder sections 52, 53 formed by free rotations 50, 51, which are connected via external grooves 56, 57 of the bush 43 to the bores 23, 24 leading to cylinders 26, 27.
  • the space 58 existing due to the free rotation 50 between the cylinder sections 52, 53 is connected via a bore 59 arranged in the bush 43 and opening into a groove 60 of the bush 43 to a relief bore 61, which extends from the end of the shaft part 40 into the space inside the cover 45 opens out.
  • Shaft part 40 has in the area of bearing point 41 an oil groove 62 which overlies a pressure oil bore 63 which is connected to the pump, so that oil via oil groove 62 and transverse bores 64, 65 and a longitudinal bore 66 in shaft portion 40 between slide 44 and bushing 43 on the one hand and slide 44 and the bottom of the bore 42 on the other hand can flow formed chambers 67, 68 and this pressurizes.
  • the cylinder sections 52, 53 close the control bores 54, 55, so that no oil can flow into or out of the cylinders.
  • the slide 44 is in the end position, in which oil can flow from chamber 68 into the control bore 55 and from there to the cylinder 27 and at the same time oil flows out of the cylinder 26, since the cylinder sections 52, 53 the control bores 54, 55 have released.
  • the oil flowing out of the cylinder 26 via the control bore 54 and the space 58 into the relief bore 61 flows into the space below the cover.
  • FIG 5 shows the slide 44 in the opposite end position, in which oil flows into the cylinder 26 via the control bore 54 and oil flows out of the cylinder 27 via the control bore 55 and the relief bore 61.
  • Steeper 44 can be of an electromagnetic or pneumatic type, the pneumatic one being operable by appropriate pressurization (possibly from a recipient or a pressure source) via an electrovalve (not shown).
  • FIG. 6 shows a section of the shaft part 4 or 40 and the drive wheel 10, in which, in one of the end positions of the angular adjustment between the drive wheel 10 and the shaft 6, a spring-loaded connecting element 69 (piston) into a recess 70 (bore) of the drive wheel 10 engages and thereby a positive connection between the drive wheel 10 and the shaft 6 is made.
  • This connection is always released when the respective cylinder is pressurized with oil pressure, ie the oil pressure acts on the connecting element 69, which is simultaneously designed as a piston, so that it is moved against the force of a spring 71 and cancels the positive connection.
  • FIG. 7 shows a block diagram from which the circuit for detecting the angular adjustment and for controlling the valves 20, 21 causing the adjustment of the device from FIGS. 1 and 2 can be seen.
  • the shaft 6 and the drive wheel 10 are shown as circles and have the pulse generators 36, 38, which generate a signal when the sensors 37, 39 are approached.
  • the signal from the pulse generator 36 of the drive wheel 10 is evaluated as a reference signal and corresponds to the maximum possible angular adjustment.
  • the signal of the pulse generator 38 of the shaft 6 leads as an actual value signal at the maximum angle adjustment to the reference signal and then has a time length which is the same as the reference signal. It is provided that the actual value signal activates a counter 40 and that the reference signal activates a further counter 41 for the signal duration and at the same time stops the counter 40 with the beginning of the signal. During their activation, the counters 40, 41 count the clocks of a clock generator 42 operating at a constant frequency. The count results are fed to a divider 43, the result of which, as a ratio of the counter results, shows the angular adjustment between the 0 and the maximum value. This result can be changed in the usual way by means of a correction value memory 44 and possibly by means of further information signals (speed, load, etc.) into a correction signal which can be supplied to the valves 20, 21 as an electrical signal via an amplifier 45.
  • Fig. 8 shows an alternative circuit, the shaft 6 having a number of pulse generators 38, the signals from the sensor 39 are counted by a counter 46 until the pulse generator 36 of the drive wheel 10 via the sensor 37 generates a signal that the counter 46 stops.
  • the counting result provides information about the angular adjustment, since a certain angular adjustment is assigned to each pulse, and can be changed into a correction signal by means of a correction value memory 47 and, if necessary, by means of further information signals, which are fed as an electrical signal to the valves 20, 21 via an amplifier 48 can.
  • the circuit according to FIGS. 7 and 8 can also be used in connection with the device according to FIG. 3, but the device then does not require a device according to FIG. 6 for the positive connection of the drive wheel 10 and the shaft 6 in the end positions of the angular adjustment.
  • the electrical signal is applied directly to this when an electromagnetic actuator is used or, when using a pneumatic actuator, to an electrovalve controlling a line connection between the actuator and a recipient or a pressure source.
  • the desired angular adjustment is locked by the slide position shown in FIG. 3, in which no oil can flow into or out of the cylinders (hydraulic locking), or by the positive connection between drive wheel 10 and shaft 6.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Vehicle Body Suspensions (AREA)
  • Gear Transmission (AREA)
  • Power Steering Mechanism (AREA)
EP85103624A 1984-04-28 1985-03-27 Vorrichtung zur Winkelverstellung einer Welle, insbesondere Nockenwelle, gegenüber einem Antriebsrad Expired EP0163046B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843415861 DE3415861A1 (de) 1984-04-28 1984-04-28 Vorrichtung zur steuerung einer kopplungseinrichtung
DE3415861 1984-04-28

Publications (2)

Publication Number Publication Date
EP0163046A1 EP0163046A1 (de) 1985-12-04
EP0163046B1 true EP0163046B1 (de) 1987-11-25

Family

ID=6234575

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85103624A Expired EP0163046B1 (de) 1984-04-28 1985-03-27 Vorrichtung zur Winkelverstellung einer Welle, insbesondere Nockenwelle, gegenüber einem Antriebsrad

Country Status (4)

Country Link
US (1) US4627825A (enrdf_load_stackoverflow)
EP (1) EP0163046B1 (enrdf_load_stackoverflow)
JP (1) JPS60234122A (enrdf_load_stackoverflow)
DE (2) DE3415861A1 (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4235929A1 (de) * 1992-10-23 1994-04-28 Rexroth Mannesmann Gmbh Zylinderverstellung

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Publication number Priority date Publication date Assignee Title
DE4235929A1 (de) * 1992-10-23 1994-04-28 Rexroth Mannesmann Gmbh Zylinderverstellung
DE4235929C2 (de) * 1992-10-23 2000-08-24 Mannesmann Rexroth Ag Zylinderverstellung

Also Published As

Publication number Publication date
DE3561080D1 (en) 1988-01-07
JPS60234122A (ja) 1985-11-20
EP0163046A1 (de) 1985-12-04
DE3415861C2 (enrdf_load_stackoverflow) 1988-08-11
US4627825A (en) 1986-12-09
DE3415861A1 (de) 1985-10-31

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