EP0628133A1 - Process for driving a device for relatively rotating a shaft and device for relatively rotating the shaft of an internal combustion engine. - Google Patents
Process for driving a device for relatively rotating a shaft and device for relatively rotating the shaft of an internal combustion engine.Info
- Publication number
- EP0628133A1 EP0628133A1 EP93922889A EP93922889A EP0628133A1 EP 0628133 A1 EP0628133 A1 EP 0628133A1 EP 93922889 A EP93922889 A EP 93922889A EP 93922889 A EP93922889 A EP 93922889A EP 0628133 A1 EP0628133 A1 EP 0628133A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- control
- pressure
- control 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2101—Cams
- Y10T74/2102—Adjustable
Definitions
- the invention is based on a method for controlling a device for the relative rotation of a shaft and a device for the relative rotation of the camshaft of an internal combustion engine with respect to the drive wheel of the same which is arranged rotatably on the camshaft.
- a piston-cylinder device is acted upon by a control valve, and the piston displaces a coupling member which is mounted in a recess in the camshaft.
- the coupling element which is in engagement with the camshaft, there are spur and helical gears, which turn the camshaft relative to the drive wheel when the adjusting piston is moved.
- a hydrostatic pump driven by the camshaft supplies the pressure medium required to adjust the actuating piston.
- the actuating piston is pressurized on two sides, one side always being pressurized by the pressure generated by the pump.
- the pressure on the other piston side is changed by the control valve by reducing the pressure or by allowing pressure medium to flow away as a function of certain control variables (control).
- the inventive method for controlling a device for the relative rotation of a shaft according to the preamble of claim 1 has the advantage that a very fast and energetically favorable mode of operation is possible. With such a method, a device for the relative rotation of the shaft of an internal combustion engine can be operated in a particularly advantageous manner, as described in claims 8 to 20.
- the device according to the invention for the relative rotation of the camshaft of an internal combustion engine according to the preamble of claim 8 has the advantage that it is simple in design and also particularly compact. It is characterized above all by a very low energy requirement.
- the oil loss is limited to leakage losses since the oil quantities to be displaced from the signal box are sucked in again by the pump.
- the adjusting element is hydraulically blocked in the rest position via the control valve; no control deviation is forced.
- the energy consumption in this embodiment is particularly low, since energy is only consumed during the adjustment.
- the entire pump revolution is used for conveying and adjusting independently of the pumping pump working space (individual pump) that is being conveyed.
- FIG. 1 shows a longitudinal section through a camshaft locking device, in FIG. 2 a section along II-II according to FIG. 1, in FIG. 3 a section along III-III according to FIG. 1, in FIGS. 4 to 7 (in each case a to e) Working diagrams of the pumps used in the device and associated valve controls ...
- 10A denotes the end part of the camshaft 10 of an internal combustion engine.
- the longitudinal bore 11 is connected to the pressure oil supply to the internal combustion engine of a motor vehicle.
- a cylindrical valve housing 13A of a control valve 13 is immersed in the depression 12, in which a slide bore 14 is formed, which in turn receives a control slide 15. The further construction of the valve was discussed later.
- a disk 16 Connected to the camshaft 10 or the flange 10B and seated on the valve housing 1A there is a disk 16, an impeller designed as a rotary piston actuator 17 with the vanes 18, 19, 20 (see FIG. 2) and a hollow cylindrical pump housing 21A of a pump 21.
- the diameter of the disk 16 corresponds approximately to that of the flange 10B, while that of the rotary piston actuator 17 is smaller.
- the end face of the pump piston facing the rotary piston actuator 17 The housing 21A is flanged outwards in the manner of a flange, its diameter corresponds approximately to that of the disk 16.
- the pump housing 21A, the rotary piston actuator 17 and the disk 16 are clamped together in a torque-proof manner by four screws 22 and connected to the flange 10B of the camshaft 10 .
- These screws 22 and the associated bores 22A start from a cylindrical recess 23 which is provided in the end face of the pump housing 21A facing away from the rotary piston actuator 17.
- the bores 22A extend into the flange 10B of the camshaft 10.
- the rotary piston actuator 17 is encompassed by a drive wheel 24 designed as a gearwheel.
- This has a cylindrical depression 24A or 24B on its end faces for receiving the flange-like end face of the pump housing 21A or the disk 16.
- the drive wheel 24 drives the camshaft 10 and the pump housing 21A (rotor of the pump 21 ) on.
- the vanes 18 to 20 of the rotary piston actuator 17 lie in corresponding recesses 25 to 27 of the drive wheel 24, which can be seen in FIG. 2, and can be rotated there by an angle of approximately 25 ° relative to the drive wheel 24.
- sealing rollers 28 are used, which are pressed by leaf springs 29 against the outer surface of the wings or against the inside of the drive wheel 24.
- These sealing rollers 28 and leaf springs 29 lie in axial grooves 30, which are each installed in the rotary piston actuator 17 and in the drive wheel 24.
- the axial grooves 30 are each arranged approximately in the middle between two vanes 18 to 20 in the rotary piston actuator 17 or in the middle of a recess 25 to 27.
- Pressure spaces 25A to 27A or 25B to 27B are delimited between the sealing rollers 28 arranged in the vanes 18 to 20 of the rotary piston actuator 17 and the sealing rollers 28 arranged in the recesses 25 to 27 of the drive wheel 24.
- the Pressure spaces 25A to 27A lie in the direction of illustration selected in FIG. 2 and viewed clockwise behind the sealing rollers 28 in the corresponding recess 25 to 27, the pressure spaces 25B to 27B in front of them.
- the rotary piston actuator 17 is penetrated by a plurality of bores 34 to 39, which are connected on the one hand to one of the pressure chambers 25A to 27A or 25B to 27B and on the other hand to annular grooves 31, 32 on the outer circumference of the cylindrical valve housing 13A.
- the bores 34, 36 and 38 each open into the annular groove 31 on the left in FIG. 1, the bores 35, 37 and 39 correspondingly into the right annular groove 32.
- these bores are the Pressure chambers 25A to 27A or 25B or 27B are acted upon or relieved, so that the rotary piston actuator 17 carries out a rotational movement either clockwise or counterclockwise.
- the camshaft 10 is set to the “early” or “late” setting of the valves of the internal combustion engine, ie. H. there is a "phase” adjustment of the camshaft relative to the drive wheel 24 or the crankshaft.
- Two radial bores 41 and 42 penetrate through the cylindrical valve housing 13A of the control valve 13 and start from the annular grooves 31 and 32.
- the radial bore 42 extends from the annular groove 32 and opens into the slide bore 14, while the radial bore 41 extends from the annular groove 31 and opens into a control annular groove 43 surrounding the slide bore 14.
- two further annular grooves 45, 46 are formed on the outer circumference of the valve housing 13A. From the - right in Figure 1 - annular groove 46 extends from a radial bore 47, which in a second control ring groove 48 on the Slider bore 14 penetrates.
- An oblique bore 49 extends from the (left) annular groove 45, which penetrates into a blind bore 50, which in turn runs parallel to the slide bore 14 and extends from the right side of the valve housing 13A or the depression 12.
- a check valve 51 is formed, which is able to open in the direction of a pressure medium flow in the direction from a chamber 52 to the oblique bore 49.
- This chamber 52 is formed between the valve housing 13A and the bottom of the recess 12.
- the blind bore 50 is penetrated by a radial bore 53, which likewise opens out on the slide bore 14 and which is covered by a sleeve 54 on the outer circumference of the valve housing 13A. This is arranged in the region of the hollow cylindrical pump housing 21A between the latter and the valve housing 13A and is firmly connected to the pump housing 21A.
- the valve housing 13A is non-rotatably connected to the rotary piston actuator 17, e.g. through an interference fit.
- the sleeve 54 and the pump housing 21a fixedly connected to it are fixed in the axial direction by means of a securing ring 56 attached to the outer circumference of the valve housing 13A, which is inserted into an annular groove 58.
- the sleeve 54 thus bears on one end face of the rotary piston actuator 17 and with its other end face on the locking ring 56.
- a further securing ring 57 is attached to the outer circumference of the valve housing 13a, which rests on the disk 16 and secures it and the rotary piston actuator 17 against displacement before it is attached to the camshaft 10.
- a cylindrical depression 61 is made in the end face of the valve housing 13A, from which the slide bore 14 extends.
- An axial bore 63 extends from the bottom 62 of the slide bore 14 and opens into the chamber 52.
- a check valve 64 is arranged in this axial bore 63 and can open when the pressure medium flows from the chamber 52 to the slide bore 14.
- the slide 15 is guided in a sliding manner in the slide bore 14. This protrudes with its one end face into the depression 61 and is provided there with an actuating ball 66.
- Two control ring grooves 67 and 68 are formed on the outer circumference of the slide 15. The control ring groove 67 - on the left in FIG.
- FIG. 3 in particular, four radially extending, continuous bores 74 to 77 are formed in the pump housing 21A, each of which is offset by 90 ° and in each of which a ball piston 78 to 81 is guided. These lie on the outside against a cam ring 82, which is arranged in a pump cover 83 closing the pump housing 21, and whose cam curve is circular and runs eccentrically with respect to the longitudinal axis of the camshaft 10.
- the pump cover 83 and with it the cam ring 82 are fixed, while the pump housing 21A rotates with the camshaft 10 - as already mentioned at the beginning.
- the pump cover 83 is connected to the surroundings or the installation space in a suitable manner. A simple claw coupling can be used for this purpose.
- the drive torque that builds up during operation can then be supported, for example, on the engine front cover of the internal combustion engine.
- an end cover 84 is fastened, through the central opening 84A of which the electromagnet 72 protrudes.
- the pump described is a double pump, that is to say two pistons which are adjacent to one another and offset by 90 ° to one another, but with their axes lying in the same plane, with their corresponding bores form the two pump elements.
- the sleeve 54 is penetrated by four pressure medium openings, of which the two pressure medium openings 87 and 88 can be seen in FIGS. 1 and 3.
- the two pressure medium openings 85 and 86 are offset in the axial direction with respect to the pressure medium openings 87 and 88 and are shown schematically in FIG. 3.
- These pressure medium openings 85 to 88 serve as input and.
- the pressure medium openings 85 and 86 connect the bores 74 and 75 to the (right) annular groove 46 and the pressure medium openings 87 and 88 connect the other two bores 76 or 77 with the (left) annular groove 45 of the control valve 13.
- the electromagnet 72 In its switching position shown in FIG. 1, the electromagnet 72 has current flowing through it, ie the plunger 72A moves the slide 15 from its (left) neutral position I to its (right) switching position II against the action of the compression spring 71.
- the control ring groove 67 in the control slide 15 and the second control ring groove 48 are connected to one another on the slide bore 14.
- the control ring groove 68 of the control slide 15 and the control ring groove 43 of the slide bore 14 are connected to one another.
- the bores 76 and 77 in the pump housing 21 are connected to the annular groove 45 via the pressure medium openings 87 and 88 and to the blind bore 50 via the bore 49.
- the slide 15 When the electromagnet 72 is not energized, the slide 15 is moved into its (left) neutral position by the action of the compression spring 71. In this neutral position, the control groove 43 is closed on one side by the control slide 15. At the same time, the control ring groove 67 of the control slide 15 is closed on one side by the wall of the slide bore 14. The pressure spaces 25A to 27A and 25B to 27B are thus also closed on one side.
- the second control ring groove 48 on the slide bore 14 and the control ring groove 68 of the control slide 15 are connected to one another.
- the two bores 74 and 75 in the pump housing 21A and the bores 76 and 77 are each connected to one another or all four bores 74 to 77 are short-circuited via the two control ring grooves 48 and 68.
- the latter are supported the lifting ring 82 attached in the fixed pump cover 83, so that they perform an upward and downward movement (suction and pressure stroke).
- the bores 76 and 77 can be released from the chamber 52 via the longitudinal bore 11 through the non-return valve 51
- Camshaft 10 can be supplied with pressure medium.
- this check valve 51 closes.
- the other two bores 74 and 75 can be filled with pressure medium via the check valve 64 which opens in the suction stroke (in the switching position II of the control slide 15 and the control valve 13 ). If the control valve 13 (control slide 15) is in its neutral position I, as already mentioned, the four bores 74 to 77 are short-circuited. Then essentially only a pressure-free pumping of the pressure medium between these four bores takes place. Pressure check losses due to leakage losses can also be compensated for in this neutral position I of the control slide 15 via the check valve 51.
- FIG. 4a shows the flow pattern of the four individual pumps Ia, Ib, Ha, Ilb, which are formed by the bores 74 to 77 together with the ball pistons 78 to 81.
- the two individual pumps Ia and Ib are formed by the bores 74 and 75 together with the ball pistons 78 and 79, are constantly connected to each other and act on the pressure chambers 25B to 27B.
- the two too Individual pumps Ha and Ilb which are constantly connected to one another are formed accordingly by the two other bores 76 and 77 together with the ball pistons 80 and 81 and act on the pressure chambers 25A to 27A.
- the flow pattern is shown over one revolution (360 °) of the pump housing 21A and begins at the zero crossing of the volume flow of the individual pump Ia, ie. H. at the top dead center of the ball piston 78.
- the three other individual pumps Ib, Ha, Ilb are each out of phase by 90 °, i. H. According to the direction of rotation shown in FIG. 3, the single pump 1b performs a suction stroke, the single pump Ha is at bottom dead center and the single pump 11b performs a pressure stroke.
- the rotary piston actuator 17 In order to bring the camshaft 10 into an "early" rotational position, ie in order to achieve early valve actuation, the rotary piston actuator 17 must be rotated with respect to the drive wheel 24 in the direction of rotation (here clockwise). For this purpose, the pressure in the pressure spaces 25B to 27B must be greater than that in the pressure spaces 25A to 27A. With the same pressure surfaces, the relative rotation of the rotary piston actuator 17 then results. For this purpose, the control valve 13 (shown schematically in FIG.
- This is activated for an adjustment of the camshaft to an "early" rotational position, ie energized when the sum of the volume flows of the individual pumps Ia and Ib becomes positive, ie when the volume flow ejected outweighs the suctioned volume flow.
- This control therefore begins at an angle of rotation of the individual pump Ia of 45 °.
- the ejected volume of the individual pump Ia is equal to the suctioned volume of the individual pump Ib.
- the suction volume of the single pump Ha and the pressure volume of the single pump Ilb also add up to zero in this phase of rotation.
- the control of the electromagnet 72 via the control device 73 is maintained over the pressure phase of both individual pumps Ia and Ib (from the angle of rotation 90 ° to 180 ° of the individual pump Ia) and continues until the sum of the volume flows becomes negative.
- This negative total volume flow begins at an angle of rotation of the individual pump Ia of 225 °. After this angle of rotation, the suctioned volume of the individual pump Ia is greater than the expelled volume of the individual pump Ib.
- the total volume flow of the individual pumps Ha and Ilb is negative over this entire rotation range (45 ° to 225 °).
- the control valve 13 By actuating the electromagnet 72, the control valve 13 is brought into its switching position II, so that the pressure volume 25B to 27B are acted upon by the total volume flow of the individual pumps Ia and Ib. At the same time, the pressure chambers 25A to 27A are connected to the individual pumps Ha and Ilb. However, their total volume flow is negative, i.e. pressure medium is drawn in.
- the rotary piston actuator 17 is accordingly rotated clockwise relative to the drive wheel 24, i.e. towards the "early" rotational position of the camshaft 10.
- the pressure spaces 25A to 27A are pressurized accordingly.
- the electromagnet 72 is controlled by the control unit 73 when the total volume flow of the two individual pumps Ha and Ilb is greater than that of the individual pumps Ia and Ib. This is the case when the angle of rotation of the individual pump Ia is between 225 ° and 405 ° or 45 °.
- the control of the electromagnet 72 takes place via the control unit 73.
- this signal or this control can take place in several cycles arranged one behind the other, each in the assigned angular range. It is also possible, in the case of relatively small adjustment ranges or correction ranges, to generate this signal or this control only over a partial range of the maximum possible angular range.
- the adjustment of the camshaft 10 in the direction of the "late” rotational position is supported in the operating state by a retroactive torque that results from the cam actuation.
- the camshaft can be adjusted in the "late” rotational position solely on the basis of this retroactive torque.
- the effect of this restoring torque results in low leakage losses in the operating state luste of the rotary leaf actuator 17 so that it is rotated accordingly.
- the electromagnet 72 - as shown in FIG. 4e by way of example - is generally activated in the early adjustment phase (angular range between 45 ° and 225 ° of the individual pump 1a) by means of short switching signals.
- the rotary piston actuator 17 is thus tracked.
- control valve is designed - as described in the exemplary embodiment above - in such a way that in its neutral position I the pressure chambers are closed on one side. As described above, the rotary piston actuator is thus hydraulically blocked except for the effects of any leakage losses.
- the so-called “early pump” (single pump Ic) is connected to those pressure chambers which, when the pressure is applied positively, cause the camshaft 10 to be adjusted early (e.g. pressure chambers 25B to 27B), the so-called “Late pump” (single pump IIc) with the pressure chambers, which bring about the late adjustment when positive pressure is applied (eg the pressure chambers 25A to 27A).
- the volume flow profiles of the two individual pumps Ic and IIc are shown in FIG. 5a, the solid line showing the volume flow profile of the individual pump Ic ("early pump”) and the dashed line the volume flow profile of the individual pump IIc ("late pump”).
- the actuation of the electromagnet 72 and thus of the control valve 13 is shown in the four switch positions below.
- the first actuation of the electromagnet shown in FIG. 5b means early adjustment
- the second actuation shown in FIG. 5c leads to a late adjustment (without leakage).
- the corresponding pressure chambers e.g. 25B to 27B
- the other pressure chambers e.g.
- the electromagnet 72 must be actuated at the times indicated in the diagram, depending on the direction of adjustment, that is, if the individual pump Ic is actuated in the angular range from 0 ° to 180 °, the early adjustment takes place, in the case of actuation in the range of 180 ° to 360 ° there is a late adjustment.
- the angular range is determined so that the angle 0 ° corresponds to the top dead center of the individual pump Ic. This angle thus corresponds to the beginning of the pressure phase of this single pump Ic. If the electromagnet 72 is not energized (neutral position I of the control valve 13, FIG. 5d), no adjustment takes place, the pumps are short-circuited and fill each other without power consumption (apart from friction and leakage losses).
- the electromagnet 72 (control valve 13) is controlled with short control pulses with the phase which counteracts the control deviation (generally in the early adjustment phase).
- the leakage quantities that occur are tracked by the two check valves 51, 64 from the engine oil circuit (FIG. 5e).
- Stroke generation also take place via an elliptical stroke ring, which generates one double stroke of each individual pump per revolution for each piston.
- the individual pumps which are each offset by 180 °, are combined. Two individual pumps arranged offset by 180 ° then act as "early pumps”, the other two individual pumps act as "late pumps”.
- the control takes place analogously to the circuit diagram explained in FIGS. 5a to 5e.
- a fundamental advantage of the devices described above for the relative rotation of the camshaft of an internal combustion engine is the very low energy requirement in comparison to other hydraulic solutions which operate according to the control principle. Energy is only absorbed during the adjustment.
- a significant noise advantage can be expected since the pistons or ball pistons are in constant contact with the stroke curve.
- the oil consumption or the oil losses in such a device are limited to leakage losses, since the oil quantities to be displaced from the rotary piston actuator are sucked in again by the individual pumps.
- the rotary piston actuator is hydraulically blocked in the rest position (when the electromagnet is not activated, neutral position I of the control valve), and no control deviation is "forced".
- pump 21 described under a) with two individual pumps Ic and IIc a very simple construction of the pump is provided by two diametrically opposed cylinder bores.
- the pump 21 shown in FIGS. 1 to 3 has a delivery volume increased by a factor of 1 with the same dimensions of the individual pumps and with a simple contour of the cam ring.
- the delivery volume is increased by a factor of 4, and a camshaft end free of lateral force is obtained by balancing the diametrically acting pump forces.
- the configuration described under c) has a delivery volume increased by a factor of 2 compared to that described under a) and also a camshaft end free of lateral force.
- the phase and direction-dependent assignment required for a defined adjustment is carried out via the control valve 13 '.
- the control valve 13 ' is also designed as a 4/2-way valve, its control slide 15' can be switched from its neutral position I to the switching position II against the action of a compression spring 71 by the electromagnet 72.
- the control slide 15 ' is designed such that the connections a and d or the connections b and c are connected from the four connections ad in the neutral position I. In switch position II, however, the connections a and c and the connections b and d are connected to one another.
- the connection c is connected to the pressure chambers (for example 25B to 27B) of the rotary piston actuator 17, which bring about an early adjustment of the camshaft when the pressure is applied positively.
- the connection d is connected to the other pressure chambers (eg 25A to 27A) of the rotary lobe actuator, which cause the camshaft to be retarded when the pressure is applied positively.
- the pump is composed of two individual pumps purple and IVa.
- the electromagnet 72 is activated in the purple in the pressure phase of the individual pump (0 ° to 180 °). In this phase, the other individual pump IVa is in its suction phase.
- the control valve 13 ' is brought into its switching position II. In this switch position II, the single pump is purple via connection a of Control valve 13 'with its connection c and thereby connected to the pressure chambers to be acted upon for an early adjustment (for example 25B to 27B).
- the individual pump IVa is connected to the other pressure chambers (25A to 27A) via the connections b and d of the control valve 13 '.
- the solenoid 72 is actuated in exactly the opposite way, i.e. the electromagnet 72 is switched off in the purple in the pressure phase of the individual pump, and purple is supplied with current in the suction phase of the individual pump.
- the actuation of the electromagnet 72 is selected such that the rotary piston actuator oscillates around the desired position.
- the electromagnet can be controlled as shown in FIGS. 6d and 6e.
- the holding phase of the rotary piston actuator or the camshaft is achieved by one control pulse per complete angular range (0 ° to 360 °).
- the control takes place in the angular range between 90 ° and 270 °.
- the electromagnet 72 is switched off.
- large control deviations are caused by such a control of the electromagnet.
- the electromagnet 72 - as illustrated in FIG. 6e - can be controlled with short control pulses. Thereby, several control pulses distributed over an entire revolution of a single pump are given to the electromagnet 72, so that the control deviations of the camshaft are counteracted.
- the timing and duration of the individual control pulses are advantageously applied such that they are the same in the pressure phase and suction phase of a single pump.
- FIG. 7a The flow rate of such a pump composed of four individual pumps is shown in FIG 7a.
- the two individual pumps IHb and HIc are connected to the connection a of the control valve 13 ', the other two individual pumps IVb and IVc accordingly to the connection b.
- the actuation of the electromagnet 72 is shown in FIGS. 7b to 7e, FIG. 7b showing the actuation required for early adjustment.
- FIG. 7c shows a control for a late adjustment of the camshaft
- FIGS. 7d and 7e show the controls of the electromagnet 72 in the holding phase.
- the electromagnet 72 is actuated in the angular range between 45 ° and 225 °.
- the electromagnet 72 is disconnected from the current over the angular range from 225 ° to 405 ° or 45 °.
- the single pump IHb is in its pressure phase, and the single pump HIc connected to it is in its suction phase.
- the suction volume of the single pump HIc and the pressure volume of the single pump IHb add up to zero at this moment.
- the control is selected so that, analogous to that described in FIG.
- the control takes place as long as the total volume flow of the individual pumps IHb and HIc is positive and at the same time the total volume flow of the individual pumps IVb and IVc is negative. If the signs of the total volume flows of the two individual pumps connected to each other are reversed (at a rotation angle of 225 ° of the individual pump IHb), the electromagnet 72 is switched off so that the control valve 13 'is moved into its neutral position I. In this neutral position I, the assignment to the individual pressure chambers is changed, as described above, so that an adjustment continues.
- the solenoid is actuated in exactly the opposite manner, i.e. it is de-energized in the angular range between 45 ° and 225 ° and is controlled in the angular range between 225 ° and 405 ° or 45 °.
- the control can take place in such a way that the correction of the control deviation goes beyond the target position, a "pendulum position" being set which fluctuates around this target value in a narrow range.
- a "pendulum position” being set which fluctuates around this target value in a narrow range.
- the last-described exemplary embodiments of the device for adjusting a camshaft with alternating assignment of the individual pumps to the pressure chambers has the advantage that the entire pump revolution for delivery and adjustment is independent of the individual pump which delivers it. In this way, with the same dimensions compared to the designs shown in FIGS. 1 to 5, adjustment which is faster by a factor of 2 can be achieved. The control deviation around the target position can be kept small with a fast electromagnet.
- the solenoid 72 is also controlled here by an electronic control unit, which detects the actual phase position of the camshaft via angle sensors, compares it with the desired value and generates a cyclically assigned clock signal taking into account the current pump position.
- the oil is supplied through the longitudinal bore 11 in the center of the camshaft and the check valve 64.
- the desired retardation when the solenoid valve is de-energized can be achieved by leakage due to the torque being passed through and additionally by way of engine oil pressure supplied to the late side by a check valve 51.
- the entire adjustment device consisting of the interlocking (rotary piston actuator), pump and control valve with electromagnet is compact as a pre-assembled unit and only has interfaces: the screwing and centering on the camshaft;
- the pump stroke curve (stroke ring) is supported by a simple claw coupling or similar and
- the described method for controlling the device for rotating the camshaft or for controlling the pressure chambers is not restricted to the rotary piston actuator described here. It is also suitable for a device for adjusting the camshaft with a sliding sleeve or an actuating cylinder. In this case, the pressure spaces acting in opposite directions should advantageously have the same volume.
- This control method and the described device for rotating a shaft can also be used, for example, in a hydraulically actuated spray adjuster for injection pumps.
Abstract
Le dispositif servant à la rotation relative de l'arbre (10) d'un moteur à combustion interne par rapport à la roue motrice (24) montée rotative sur cet arbre comporte une pompe hydrostatique (21) dont le carter (21A) est solidaire en rotation à l'arbre à cames (10). A l'intérieur de la roue motrice (24) et de la pompe (21), une soupape de commande à commande électromagnétique (13, 13') commande les liaisons hydrauliques entre la pompe et le dispositif de réglage (commande à piston rotatif) (17), c'est-à-dire alimente ou décharge les chambres de pression (25A à 27A, 25B à 27B), ce qui provoque une rotation correspondante de l'arbre à cames par rapport à la roue motrice. L'électro-aimant (72) de la soupape de commande (13, 13') est actionné par un appareil de commande (73) influencé par des capteurs. L'alimentation en fluide sous pression se fait en direction du dispositif de réglage à travers un alésage (11) dans l'arbre à cames (10). On obtient ainsi un dispositif de réglage très compact pour l'arbre à cames.The device serving for the relative rotation of the shaft (10) of an internal combustion engine relative to the drive wheel (24) rotatably mounted on this shaft comprises a hydrostatic pump (21) of which the casing (21A) is integral in rotation with the camshaft (10). Inside the drive wheel (24) and the pump (21), an electromagnetically controlled control valve (13, 13 ') controls the hydraulic connections between the pump and the adjustment device (rotary piston control) (17), that is to say supplies or discharges the pressure chambers (25A to 27A, 25B to 27B), which causes a corresponding rotation of the camshaft relative to the drive wheel. The solenoid (72) of the control valve (13, 13 ') is actuated by a control device (73) influenced by sensors. The pressurized fluid is supplied to the adjustment device through a bore (11) in the camshaft (10). This gives a very compact adjustment device for the camshaft.
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4237193A DE4237193A1 (en) | 1992-11-04 | 1992-11-04 | Method for controlling a device for the relative rotation of a shaft and device for the relative rotation of the shaft of an internal combustion engine |
DE4237193 | 1992-11-04 | ||
PCT/DE1993/001005 WO1994010429A1 (en) | 1992-11-04 | 1993-10-22 | Process for driving a device for relatively rotating a shaft and device for relatively rotating the shaft of an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0628133A1 true EP0628133A1 (en) | 1994-12-14 |
EP0628133B1 EP0628133B1 (en) | 1997-08-06 |
Family
ID=6472056
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP93922889A Expired - Lifetime EP0628133B1 (en) | 1992-11-04 | 1993-10-22 | Process for driving a device for relatively rotating a shaft and device for relatively rotating the shaft of an internal combustion engine |
Country Status (6)
Country | Link |
---|---|
US (1) | US5450825A (en) |
EP (1) | EP0628133B1 (en) |
JP (1) | JP3325575B2 (en) |
KR (1) | KR100307279B1 (en) |
DE (2) | DE4237193A1 (en) |
WO (1) | WO1994010429A1 (en) |
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1992
- 1992-11-04 DE DE4237193A patent/DE4237193A1/en not_active Withdrawn
-
1993
- 1993-10-22 US US08/256,309 patent/US5450825A/en not_active Expired - Lifetime
- 1993-10-22 WO PCT/DE1993/001005 patent/WO1994010429A1/en active IP Right Grant
- 1993-10-22 JP JP51054894A patent/JP3325575B2/en not_active Expired - Fee Related
- 1993-10-22 DE DE59307077T patent/DE59307077D1/en not_active Expired - Fee Related
- 1993-10-22 KR KR1019940702330A patent/KR100307279B1/en not_active IP Right Cessation
- 1993-10-22 EP EP93922889A patent/EP0628133B1/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
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See references of WO9410429A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO1994010429A1 (en) | 1994-05-11 |
JP3325575B2 (en) | 2002-09-17 |
KR100307279B1 (en) | 2002-02-28 |
EP0628133B1 (en) | 1997-08-06 |
US5450825A (en) | 1995-09-19 |
JPH07506885A (en) | 1995-07-27 |
DE59307077D1 (en) | 1997-09-11 |
DE4237193A1 (en) | 1994-05-05 |
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