WO2003083269A1 - Vorrichtung zur umwandlung einer drehbewegung in eine hin- und hergehende bewegung - Google Patents
Vorrichtung zur umwandlung einer drehbewegung in eine hin- und hergehende bewegung Download PDFInfo
- Publication number
- WO2003083269A1 WO2003083269A1 PCT/AT2003/000050 AT0300050W WO03083269A1 WO 2003083269 A1 WO2003083269 A1 WO 2003083269A1 AT 0300050 W AT0300050 W AT 0300050W WO 03083269 A1 WO03083269 A1 WO 03083269A1
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- WIPO (PCT)
- Prior art keywords
- cam
- enclosing
- control
- carrier shaft
- length
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/08—Shape of cams
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/30—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of positively opened and closed valves, i.e. desmodromic valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0057—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by splittable or deformable cams
Definitions
- the invention relates to a device for converting a rotary movement into a reciprocating movement, in particular cam control, valve train for internal combustion engines of motor vehicles or the like, with a carrier shaft and with at least one control cam area, wherein in each control cam area a rotatably driven cam element having an eccentric control surface and a cam follower element, in particular a valve tappet or the like, which is displaceable or pivotable by the cam element, is provided, the cam element being rotatably arranged in a flexible enclosing element which is connected to the cam follower element.
- WO 01/12958 A and WO 01/12959 A Various versions of this type of positive guidance are described in WO 01/12958 A and WO 01/12959 A.
- the encircling element surrounds the circumference of the cam element without significant play, so that it is adapted to the shape of the cam, and the cam element can twist in the latter due to the nature of the encircling element. Since the encircling element connected to the valve actuator cannot rotate with the cam element, the movement of the cam region around the axis of rotation of the cam element is converted into a reciprocating or reciprocating movement of the cam follower element which is displaceably or pivotably mounted in the cylinder head.
- the cam follower element does not move as long as the connection area of the enclosing element with the cam follower element on the base circle area of the rotating cam element rests, is then removed from the axis of rotation of the cam element in the radial direction and finally returned, while the cam area of the cam element passes the connection area of the enclosing element with the cam follower element.
- variable valve control has become known for a large number of different constructions, by means of which the opening and closing times and the stroke of the valve can be changed in order to improve the performance, the exhaust gas behavior, the fuel consumption, the torque, etc. of an internal combustion engine Compared to the non-adjustable valve control with fixed values, the filling of a cylinder is improved if the valve opens later and closes earlier at low speeds, opens earlier and closes earlier at higher speeds, and if the stroke is varied. to optimize the exhaust gas behavior, the torque, the engine power, etc. by adjusting the valve control, in particular depending on the load and / or speed, etc.
- the variable valve controls usually change the position of the actuating surface of the cam follower element relative to the eccentric valve control surface or to the axis de r carrier shaft (WO 98/26161) by twisting, shifting or enlarging the cam element.
- variable control is already described in the mentioned WO 01/12959, only the enclosing element being reversibly changeable there.
- the non-changeable rotating cam element generates speed-dependent increasing tensile forces at the connection point with the cam follower element, so that the encircling element, which is free of play at the circumference of the cam element at a low speed, lifts away from the circumference with increasing speed, and thereby occupies positions, the cam elements with greater circumferential lengths correspond.
- the stroke of the cam follower element is thus increased depending on the speed.
- the enclosing element has at least a limited length-elastic partial area
- the enclosing element is not elastic, but longer than the enclosing element, and the protrusion is accommodated in a protuberance, with an elastic change in size the protuberance is provided.
- the invention has now set itself the task of allowing variable control in a device of the type mentioned despite the circumferential surrounding element substantially free of play.
- the length of the enclosing element and the circumferential length of the cam element can be changed in unison.
- the term mutable can be understood to mean that the enclosing element at any time surrounds the cam element essentially without play, it being irrelevant which of the two lengths serves as the manipulated variable for the second length.
- Both the circumferential length of the cam element can be variably changed in accordance with the length of the enclosing element, and the enclosing length of the enclosing element can be designed to be adaptable to the respective circumferential length of the cam element.
- the active adjustment of the cam element enables an enlarged adjustment range, since a zero stroke can be selected as the output, in which the parts of the cam element are fitted into one another within a circular circumferential contour.
- the zero stroke is important, for example, when it should be possible to be able to deactivate individual valves of an internal combustion engine.
- the cam element on the carrier shaft can preferably be extended and retracted in a radial plane without changing a part comprising the basic position contact surface of the control cam region.
- the part comprising the basic position contact surface is provided on the carrier shaft and rotates with it.
- the carrier shaft is hollow and accommodates a control shaft on which a control surface which at least causes the cam element to extend is provided in the control cam region.
- the control shaft can be longitudinally displaceable in the carrier shaft and can have an inclined surface which interacts with a corresponding inclined surface on the cam element.
- the control shaft can be rotatably arranged in the carrier shaft and can have a spiral control surface which interacts with an inwardly projecting web or the like of the cam element.
- a third embodiment in which the control shaft can also be rotated in the carrier shaft, provides that the cam element is arranged so as to be pivotable about an axis parallel to the axis of rotation of the carrier shaft and is provided with a guide surface which interacts with a crank pin of the control shaft. If the cam element is pivoted, the cam profile is changed asymmetrically. In the case of a valve train, there are also different opening and closing properties.
- the carrier shaft can itself be used as a control shaft if it is arranged in a longitudinally displaceable manner in at least two bearing elements and has an inclined surface which interacts with an inclined surface of the cam element, the cam element being held axially immovably, for example by the two bearing elements.
- the movement of the cam element in the radial plane can also be positively guided, so that the cam element is drawn back into the carrier shaft by the actuating mechanism.
- the frictional relationships can be significantly improved if the carrier shaft and the cam element have feed channels for a friction-reducing medium to the eccentric control surface.
- an enclosing element that can be changed in enclosing length is formed from an expansion-resistant material and has a circumferential length corresponding to the maximum circumferential length of the cam element, the difference between the enclosing length and the circumferential length of the enclosing element being in at least one variable indentation or protuberance is arranged.
- the formation of a variable indentation or protuberance is possible because the enclosing element is prevented from rotating due to its connection with the cam follower element, so that the indentation or protuberance can be provided in a stationary manner at any location around or into the cam element.
- the indentation or protuberance can be elastically resilient, and in particular can be acted upon by a spring or the like, or can be adjusted by a hydraulic element or the like.
- the protuberance is provided with an elastically flexible constriction.
- the enclosing element can have parts made of different materials, at least one material being elastically stretchable.
- the stretchable parts make the protuberance that is provided with stretch-resistant materials superfluous.
- a preferred embodiment of an expandable enclosing element or a combination of expandable and expandable parts is realized by a multi-link element, in particular by a chain, which has side plates connected by articulated pins and optionally rollers.
- the spring causing the protuberance engages between two non-consecutive hinge pins of the chain, whereby an intermediate hinge pin is skipped.
- the spring is a tension spring, the hinge pin in between is pushed up by the circumference of the cam and forms the protuberance, the tabs being inclined on both sides.
- the spring is formed by a spring sheet metal strip which is guided over the skipped hinge pin and with its ends engages under the two hinge pins. Two protuberances are formed here, since each of the two articulated pins under engagement is pushed up from the circumference of the cam.
- the tabs are resilient and are preferably formed from a spring wire, plastic, rubber or the like to form a frame-like element which encloses two hinge pins and is pretensioned in order to shorten the distance between the hinge pins.
- the tab is therefore stretched as the cam circumferential length increases and shortens as it decreases. The difference in length to be achieved is small if each plate of the closed chain is designed to be resilient.
- a compression spring element for example made of rubber, can spread apart the opposite sides in each tab, so that the length of the tabs changes even with flexible, non-elastic material.
- the stretched position can each represent an expansion limitation, so that the maximum stroke length is not exceeded, even if speed-related additional tensile forces from the cam follower element articulated on the enclosing element become effective.
- the enclosing element consists of an elastically stretchable material, an expansion limitation preferably also being associated with this enclosing element.
- the encircling element can be a band made of a textile-bound sheet material, in particular a fabric or the like produced in a rounding technique, which is stretchable, whereby woven or additionally stretch-resistant threads, the length of which corresponds to the length of the maximum cam circumference, are provided.
- the differential length is stored in at least one spring-loaded protuberance. Since the encircling element is particularly exposed to relatively high tensile forces from the reciprocating cam follower element when the repulsion acceleration is braked, that part of the encircling element opposite the connection area is pressed firmly onto the circumference of the cam element. Conversely, the part of the enclosing element enclosing the connection area is exposed to correspondingly high compressive forces shortly before returning to the starting position, since the return acceleration is braked, and pressed onto the circumference of the cam element.
- outlet openings lying in these areas are sealed by the enclosing element, and a very high pressure would be required to supply the lubricant.
- a pressure of 2 to 5 bar is present in conventional cylinder heads, and at least 10 times the pressure should be able to be applied in order to push the enclosing element away from the circumference and to allow the medium to escape.
- the values in this example refer to oil lubrication). Only partial lubricant films are created and mixed friction occurs, the coefficient of friction of which does not become less than 0.1.
- the flexible encircling element Since the flexible encircling element is prevented from rotating, the friction conditions can be improved even further in a further embodiment if the flexible encircling element surrounds the eccentric control surface of the driven cam element and a non-driven basic contact surface for the cam follower element.
- a non-driven contact surface is primarily understood to mean a cylindrical contact surface fixed to the device, for example on a bearing element of the carrier shaft. In this way, depending on the shape of the cam, the length of the contact area between the cam element and the enclosing element, which generates a substantial part of the friction, can be reduced in length by at least one third, and in conventional cam shapes even by up to two thirds.
- the friction-generating contact surface is also narrower than in the embodiments mentioned at the beginning.
- the non-driven contact surface can also on one, for example on the
- Bearing element rotatably mounted ring or the like. Be formed, so that a minimal back and forth rotation of the contact surface is possible, which is due to the slightly vigorously alternating geometric relationships between the connection point of the enclosing element with the cam element and the moving control surface.
- Further measures to reduce friction can be the arrangement of rolling bearings between each bearing element and the carrier shaft and / or the cam element, and / or the arrangement of a rotatably mounted roller in the eccentric control surface of the cam element and / or the formation of feed channels for a friction-reducing medium, in particular lubricating oil, to the friction-generating contact surfaces.
- the reduction in the friction-generating contact surfaces further reduces the amount of heat that is generated, the removal of which is facilitated if the standing base circle area is part of the camshaft bearing and can be connected directly to the housing, in particular the cylinder head, and reduces the need for lubricant.
- a small restoring force acting on the cam follower element can be advantageous.
- the restoring force can act on the bearing pin in that the bearing pin is acted upon by an elastic element against the contact surface fixed to the device.
- a leg spring or the like can be used to generate the restoring force, which is supported on the one hand on the bearing pin and on the other hand on the bearing element or the like.
- the bearing pin has at least one exposed end area and an elastically flexible band made of steel, rubber or the like is guided around the exposed end area and the bearing element.
- Fig. 1 is a perspective view of components of a first
- FIGS. 2 to 4 longitudinal sections through the first embodiment, FIG. 2 showing a zero stroke position, FIG. 3 a normal stroke position and FIG. 4 a maximum stroke position, FIGS. 5 and 6 zero stroke and maximum stroke position of a second embodiment, 7 and 8 zero stroke and maximum stroke position of a third embodiment, FIG. 9 oblique views of the carrier shaft and the cam element in three different positions of a fourth embodiment, FIG. 10 a longitudinal section similar to FIG. 4 through the embodiment according to FIGS. 9, 11 and 12 Longitudinal sections through a fifth embodiment of the device according to the invention, the cam follower in each case abutting the contact surface, FIGS. 13 and 14 schematic sections along the line Xlll-Xlll of FIG.
- FIG. 17 shows a control shaft le a seventh version in oblique view
- Fig. 20 shows a section through the line XX-XX of Fig. 18,
- FIG. 23 shows a schematic end view of the eighth embodiment in the normal stroke position
- FIG. 24 shows a schematic oblique view of the protuberance spring from FIG. 23,
- FIG. 28 a schematic end view of a twelfth embodiment in the normal stroke position
- FIG. 29 a first embodiment of a link plate of the twelfth embodiment
- 30 and 31 a second embodiment of the link plate in the normal stroke and in the maximum stroke position
- FIG. 32 is a schematic illustration of a thirteenth embodiment
- Fig. 33 components of a fourteenth embodiment in an oblique view
- the eccentric control surface 4 reciprocates a cam follower element 10, which is held against it, in accordance with its guidance or mounting.
- the preferred application of the device is shown in all exemplary embodiments, namely as valve control of internal combustion engines. However, the use of such devices can also serve, for example, in cam controls of machine tools, in special gearboxes or the like, the cam follower element 10, which forms a valve lifter in the exemplary embodiments shown, being designed in accordance with the application.
- valve train for a valve
- a valve train used for an internal combustion engine of a motor vehicle on a driven carrier shaft 1 having the number of cam elements 71 required for the valves.
- Each control cam area 2 comprises a base circle area 3, 53 and an eccentric end face 4, which is provided on a cam element 71, and is surrounded by a substantially adjacent encircling element 6, so that the cam element 71 with continuous pulsating deformation of the encircling element 6 in the encircling element 6 can be driven about the axis of rotation 8.
- the cross-sectional shape of the enclosing element 6 is shown in each case in the figures adapted to the cam element 71, since here the valve train is shown in an exploded view, while as a loose individual element it has the shape of a collapsed oval or the like.
- the encircling element 6 is prevented from rotating by the connection to a cam follower element 10, which in the case of a valve tappet in a guide sleeve 41 of the cylinder block 80, in the case of a rocker arm or rocker arm, is pivotally mounted in a pivot bearing.
- the encircling element 6 is connected to the cam follower element 10 so that it can be pivoted or pivoted about an axis 15, so that when the cam element 71 passes through the connecting region of the cam follower element 10, the encircling element 6 can be pivoted relative to the cam follower element 10.
- the cam follower element 10 is transferred from the system on the base circle surface 3, in which it has the shortest distance to the axis of rotation 8, into a position which is at a maximum distance from the axis of rotation 8 when the maximum of the eccentric control surface 4 of the cam element 71 is effective, and at the further rotation is pulled back into the basic position.
- this up and down movement represents the valve stroke, the length of the stroke being adjustable as a function of speed and / or load, as will be explained further below.
- the guide sleeve 41 and the valve stem 11 are shown in radial alignment with the axis of rotation 8.
- Such an embodiment has asymmetrical opening and closing properties with respect to a symmetrical cam element 71, which can be advantageous in certain applications.
- the enclosing element 6 can either be elastically stretchable and pretensioned for contraction, or have a maximum circumferential length, the respective excess with a small valve lift in a “store”, for example in the form of a protuberance.
- An elastically stretchable encircling element 6 can be, for example, a band produced in a textile rounding technique, which is preferably associated with a stretch limitation by threads made of Kevlar, glass, carbon, high-modulus polyethylene extending in the stretchable material or parallel to it in the circumferential direction of the cam element -, Polyester, boron, aramid fibers or similar, substantially constant-length fibers, or combinations of these fibers are provided.
- the elastic stretch can be selected to be linear, progressive or degressive, for example by incorporating threads with different stretching properties, which act simultaneously or in succession.
- Particularly suitable materials for an enclosing element having at least elastically stretchable partial areas have an elastic modulus between 1 and 4000 N / mm 2 .
- Rubber-like materials have low moduli of elasticity and are preferably provided with an expansion limit.
- Materials, such as plastics with higher moduli of elasticity, in particular between 600 and 2000 N / mm 2 , preferably between 800 and 1200 N / mm 2 generally do not require any stretch limitation, which of course can nevertheless be provided.
- the control cam area 2 comprises a cam part 70 connected to the carrier shaft 1 in a rotationally fixed manner and a cam element 71.
- the cam part 70 has a cylindrical basic shape with the base circle area 3 and a central window 75, which is somewhat less than half the circumference, two cam areas 43 on both sides circular outer contour remain.
- a rotating control rod 64 is axially displaceable in the carrier shaft 1 and has a control section 66 with an axially increasing inclined surface 67 in the region of each cam element 71.
- the cam element 71 of the cam element 2 which also has an inclined surface 72, bears on the inclined surface 67 exposed in the window 75, on which the eccentric control surface 4 is provided and which is guided in the window 75 between the lateral cam regions 43. 2 to 4 show different positions.
- the control rod 64 is shifted to the left so far that the cam element 71 reaches its lowest position, in which it lies within the circular outer contour of the cam part 70. In this position, the rotation of the cam element 71 also does not cause a valve lift.
- the cam follower element 10 guided in the guide sleeve 41 of the cylinder block 80 or the like remains in the Closed position, and the enclosing element 6 is not extended. An associated cylinder of the internal combustion engine is therefore out of function.
- control rod 64 is shifted to the right by an actuation mechanism (not shown) (arrow 81), then a normal stroke position is given in a position according to FIG. 3, as is favorable, for example, for the idling speed or a lower speed range, the cam element 71 being pushed out radially is.
- the elastic encircling element 6 in this embodiment is extended by a certain amount partly due to the extension of the cam element 71 and partly due to the tensile forces acting at idle speed in the direction of the valve stem 11, the increase in the distance between the axis of rotation 8 and the holder 12 extending the extension of the cam element 71 corresponds.
- the cam element 71 lies within the cylindrical outer surface of the cam part 70, so that the contracted enclosing element 6 bears all around on the cam part 70. Due to the elasticity of the encircling element 6, it can be advantageous if it contains stiffeners in the transverse direction, that is to say in the axial direction of the carrier shaft 1, for example in the form of reinforcing ribs 63 which have, for example, inserted or glued-in pins. The transverse stiffeners prevent the drawing of unsupported parts of the enclosing element 6 into free spaces 73 of the control cam region 2 resulting from the interlocking of the cam part 70 and the cam element 71.
- FIG. 7 and 8 show a cam element 71 which carries the eccentric control surface 4 and which is pivotably mounted on the cam part 70 about an axis 77 parallel to the axis of rotation 8.
- the pivoting takes place via a crank pin 76 of the carrier shaft 75, which pivots the cam element 71 from the zero stroke position according to FIG. 7 while extending the enclosing element 6 into the maximum stroke position according to FIG. 8 (arrow 83).
- the eccentric control surface 4 of the cam element 71 which lies within the circular circumferential contour of the cylindrical cam part 70 in FIG. 7, gives the control cam region 2 an asymmetrical shape, so that the opening and closing properties of the valve are different for each stroke size.
- the choice of the curved shape of the cam element 71 preferably results in a swiveled-out position in which the control cam region 2 is symmetrical (FIG. 8). However, this does not have to be the maximum stroke position.
- control cam area 2 comprises elements which also rotate about the axis of rotation 8.
- the base circle region 3 is provided on an element that does not rotate, which therefore has a fixed basic position contact surface 53 for the cam follower element 10.
- the bearing elements 16 are shown as tubular pieces with ring-like end regions 17, which are fixed, for example, in mountings fixed to the housing, or are provided with corresponding fastening parts.
- the cam element 71 has the eccentric control surface 4, the axial extent of which around the two annular end regions 17 of the bearing elements 16 is shorter than the width of the enclosing element 6.
- the enclosing element 6 thus surrounds part of the cylindrical peripheral surface of the two end regions 17 and the eccentric control surface 4 of the cam element 71. Since only the eccentric control surface 4 has to slide on the inner surface of the enclosing element 6, the friction-generating contact surface is smaller than half the inner surface of the enclosing element 6.
- this is connected in an articulated manner to the cam follower element 10 via its holder 12, so that no friction occurs between the enclosing element 6 and the cylindrical outer surface of the two end regions 17 serving as contact surface 53, which are fixed to the housing as parts of the bearing elements 16.
- the hinge axis 15 runs parallel to the axis of rotation 8 of the carrier shaft 1.
- the rotation of the cam element 71 leads to an oscillating movement of the enclosing element 6 which, thanks to its connection to the cam follower element 10, is continuously lifted all around from the outer surface of the end region 17.
- the cam follower element 10 is thereby transferred from the contact surface 53, in which the cam follower element 10 has the shortest distance to the axis of rotation 8, and which forms part of the outer surface of the end region 17, into a position which is at a maximum distance from the axis of rotation 8 when the maximum of the eccentric Control surface 4 of the cam element 71 is effective, and retracted into the basic position during further rotation.
- the closed position is the basic position and the maximum removed position is the open position of the valve plate 13.
- a central hub-like region 14 of the carrier shaft 1 is preferably rotatably supported on both sides in a bearing element 16 for each control cam region 2.
- the area 14 has a cutout 5 which is provided with an inclined surface 7 which rises in the longitudinal direction and lateral parallel flats.
- the cam element 71 is provided with an approximately U-shaped cut-out on the side opposite the eccentric control surface 4 and is guided in a vertically extendable and retractable manner on the parallel flats.
- an extended bearing pin 48 is inserted into the holder 12 of the enclosing element 6, on which a cam follower element 10 is rotatably mounted on both sides.
- the ends 61 of the bearing pin 48 each protrude through a slot 87 in brackets 85 and are urged against the bearing elements 16 by a band made of rubber, a clip made of spring steel or another elastic element 31.
- the lateral sliding of the element 31 is prevented by a covenant.
- the elastic elements 31 are stretched by the cam element 71 during the downward movement of the cam follower elements 10, that is to say when the valves are opened, and generate a force that supports the return, which can be advantageous in some applications.
- FIG. 14 clearly shows that the cam element 71, which does not protrude over the circumference of the bearing element 16 in a lowest position, is lifted from the wedge-shaped inclined surface 7 when the carrier shaft 1 is shifted to the left and is transferred to the maximum extended position shown in FIG. 13.
- the elastic enclosing element 6 can dispense with the elastic elements 31 shown in FIGS. 11 and 12, since it also exerts a restoring force on the bearing pin 48. Due to the elasticity of the enclosing element 6, it can be advantageous if it contains stiffeners in the transverse direction, that is to say in the axial direction of the carrier shaft 1, for example in the form of reinforcing ribs 63 which have inserted or glued-in pins. The cross stiffeners prevent the pulling in of unsupported parts of the enclosing element 6 in the region of the cam element 71.
- FIG. 15 and 16 show an embodiment in which the cam element 71 is forcibly extended and retracted.
- a control shaft 94 in the interior of the carrier shaft 1 has a slot 95 in which a link 98 is rotatably mounted on a bearing journal 96.
- the second end of the link 98 is arranged on a bearing journal 97 which is mounted in the interior of the cam element 71, the cam element 71 being approximately U-shaped and extending in a guide of the carrier shaft 1 or a guide sleeve arranged on the carrier shaft 1. and is arranged insertable.
- the positive guidance thus represents a crank mechanism that can be rotated through an angle of approximately 120 °.
- FIG. 15 shows a partial stroke
- FIG. 16 shows the full stroke of the cam element 71.
- the enclosing element 6 forms a rectilinear bridging of the transition region between the two sides on both sides rotatable contact surface 53 and the eccentric control surface 4, which changes when the stroke changes.
- the enclosing element 6 used in FIGS. 17 to 27 and 32 to 34 is stretch-resistant, so that the respective differential length between the enclosing length of the control cam region 2 and a circumferential length corresponding at least to the maximum stroke must be stored.
- 17 to 21 show an embodiment similar to FIGS. 1 to 4 with a control rod 64 which is longitudinally displaceable in the carrier shaft 1 and which has a control section 66 which is flattened on both sides and has an inclined slope for each control cam region 2
- the carrier shaft 1 is provided in each control cam area 2 with two circumferential ribs 22, between which a guide groove for the
- Cam element 71 is formed, and between which the carrier shaft 1 is partially cut. In the windows 75 formed similar to FIG. 1 is the cam element
- Cam element 71 when moving the control rod 64 in both directions.
- the pin 79 is arranged in a slide 62 which is connected to the
- Sloping surfaces 67 of the longitudinal slot 60 slides along.
- the encircling element 6 is in each case formed by a multi-link element, in particular by a chain 21, the hinge pins 23 of which connect side plates 24, which also effect the axial guidance on the cam element 71 engaging between the plates 24 ,
- the chain 21 in the embodiments according to FIGS. 17 to 27 represents an extensible enclosing element 6, which is turned over to adjust the enclosing length.
- One or two hinge pins 23 or rollers 25 can be lifted from the cam circumference, the tabs 24 being raised in a roof-like manner by spring action, as can be seen from the different exemplary embodiments in FIGS. 23 to 27.
- the height of the circumferential ribs 22 on the carrier shaft 1 is selected at least so that the hinge pins 23 or the rollers 25 bear against the circumferential ribs 22, and the Straps 24 overlap the peripheral rib 22 on the outside, so that the chain 21 is axially fixed in the control cam region 2.
- the carrier shaft 1 can have inlet bores 19 in the bearing areas 9 for supplying a lubricant to the cam element and to the chain links.
- the associated section of the control rod 64 has a circumferential groove 88, the length of which corresponds at least to the displacement length of the control rod 64, and lead from the transfer channels 89 into the flattened control sections 66.
- the lubricant entering through the bores 19 passes through the circumferential groove 88, the transfer channels 89 and the control section 66 on the one hand into the longitudinal slot 60 to its inclined surfaces 67 and on the other hand through the windows 75 between the circumferential ribs 22 and on the outer surfaces of the cam element 71 to the individual chain links which are evenly supplied with the lubricant by the cam element 71 rotating in the chain 21.
- a storage of the respective excess length is necessary in the case of a stretch-proof enclosing element 6, which in the case of a chain 21 can take place, for example, by fitting the chain in a suitable area of the circumference. 21 to 24, two spring strips 35 are provided for this purpose, which run over a central hinge pin 23 and engage under the two subsequent hinge pins 23.
- the spring strips 35 are pretensioned in such a way that they lift up the two articulated pins 23 under which the cam element 71 is drawn in. 22 shows the maximum stroke position in which the chain 21 lies all around, and FIG. 23 shows a normal stroke position.
- FIG. 25 shows triangular hinge plates 26, a tension spring 40 being inserted between the upstanding ends, which acts on two protuberances 34. 27, the tension spring 40 is arranged between a hinge pin 23 and the hinge pin 23 next to it, so that a protuberance 34 is formed between these two hinge pins and the middle hinge pin 23 is pulled up.
- the tension spring is further tensioned when the cam element 71 is extended into the maximum stroke position.
- Actuable hydraulic piston-cylinder units can be used.
- the length of the chain can be adapted to the smallest circumferential length of the control cam region 2 by means of a piston-cylinder unit, such a piston-cylinder unit also being able to replace a chain link or a pair of plates.
- At least one hinge pin 23 can be provided with an eccentric region, not shown, so that the rotation of the hinge pin changes the distance to the next hinge pin 23.
- Fig. 29 shows a frame-like tab 24 made of a flexible material, which loops around the two hinge pins 23.
- a spring 32 is arranged between the two long sides and spreads the long sides apart. The tabs 24 can therefore be stretched in the circumferential extension, so that the chain 21 becomes longer, and shorten when the cam element 71 is pulled in.
- the spring 32 can be of any design, and not only be formed by the compression spring shown schematically, but also by one Rubber pads or the like
- FIG. 30 and 31 show a frame-like tab 24 made of a resilient material, for example spring wire or the like, which is pretensioned to shorten the distance between the hinge pins 23 (FIG. 30).
- a resilient material for example spring wire or the like
- each tab 24 is stretched into the end position shown in FIG. 31.
- the tabs 24 can also be cast into a rubber-like material or vulcanized thereon.
- rollers 25 which are mounted on the hinge pins 23.
- the rollers can, for example, be made from a highly wear-resistant, low-friction ceramic, for example from silicon nitride (Si 3 N 4 ).
- sliding bodies can also be provided.
- a hinge pin is extended and forms the bearing pin 48 for the fork-shaped holder 12 of the cam follower element 10, into which the valve stem 11, which is provided with a thread 28, is adjustably screwed and fastened by the lock nut 27.
- the holder 12 is formed by a triangular hinge axis in which the cam follower element is articulated on an additional bearing pin 48.
- the enclosing element shown in FIGS. 32 to 34 is in turn stretch-proof and designed as a band or the like.
- 32 shows a schematic possibility of storing the tape in that the excess length in the form of a protuberance 34 is guided over two deflection rollers 36 which are parallel to one another and kept at a distance and over a deflection roller 38 which is operated, for example, by means of a spring 30, a hydraulic piston Cylinder unit or the like. Is applied to the outside.
- the length of the enclosure is increased by extending or pivoting the cam element 71, a piece of the enclosure element 6 is drawn out of the protuberance 34, as a result of which the spring 30 is compressed to a greater extent.
- the spring 30 pushes the deflection roller 38 further outward.
- the protuberance 34 has a constriction 37 of the enclosing element 6, which is designed to be elastically flexible.
- the solid lines of the enclosing element 6 show the normal stroke position.
- the maximum stroke position in which the eyelet 47 accommodating the holder 12 is further spaced from the axis of rotation 8, is drawn with broken lines with expanded constriction 37.
- the insert 54 inserted into the protuberance 34 has a latching or threaded bore 57 into which the latchable or threaded end 28 of the valve stem 11 can be inserted or screwed.
- a lock nut 27 is used to adjust or set the length of the cam follower element 10.
- the forces acting when the cam part 71 is pushed out expand the constriction 37, the areas of which touching one another move away from one another.
- the constriction 37 is provided by two clamping jaws 49 which can be clamped together by springs 33.
- the two clamping jaws 49 can also be of the same design, so that a connecting screw is inserted into a clamping jaw 49. If necessary, the bias of the springs 33 can also be adjustable.
- a latchable, elastically expandable stripping device is also conceivable, for example by clipping two identically designed parts provided with latching hooks and latching openings.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Transmission Devices (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE20320710U DE20320710U1 (de) | 2002-03-28 | 2003-02-17 | Vorrichtung zur Umwandlung einer Drehbewegung in eine hin- und hergehende Bewegung |
AU2003208163A AU2003208163A1 (en) | 2002-03-28 | 2003-02-17 | Device for converting a rotational displacement into a displacement back and forth |
US10/949,913 US6968814B2 (en) | 2002-03-28 | 2004-09-24 | Device for converting a rotational movement into a reciprocating movement |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/AT2002/000096 WO2003014535A1 (de) | 2001-08-06 | 2002-03-28 | Vorrichtung zur umwandlung einer drehbewegung in eine hin- und hergehende bewegung |
ATPCT/AT02/00096 | 2002-03-28 | ||
US10/213,625 US6802287B2 (en) | 1998-06-16 | 2002-08-06 | Valve mechanism, in particular for internal combustion engines |
US10/213,625 | 2002-08-06 | ||
AT17282002 | 2002-11-15 | ||
ATA1728/2002 | 2002-11-15 |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/AT2002/000096 Continuation WO2003014535A1 (de) | 2001-08-06 | 2002-03-28 | Vorrichtung zur umwandlung einer drehbewegung in eine hin- und hergehende bewegung |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/949,913 Continuation US6968814B2 (en) | 2002-03-28 | 2004-09-24 | Device for converting a rotational movement into a reciprocating movement |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2003083269A1 true WO2003083269A1 (de) | 2003-10-09 |
Family
ID=28678469
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/AT2003/000050 WO2003083269A1 (de) | 2002-03-28 | 2003-02-17 | Vorrichtung zur umwandlung einer drehbewegung in eine hin- und hergehende bewegung |
Country Status (3)
Country | Link |
---|---|
AU (1) | AU2003208163A1 (de) |
DE (1) | DE20320710U1 (de) |
WO (1) | WO2003083269A1 (de) |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004026430B3 (de) * | 2004-05-29 | 2005-09-01 | Dr.Ing.H.C. F. Porsche Ag | Ventiltrieb für eine Brennkraftmaschine |
EP1580405A1 (de) * | 2004-03-26 | 2005-09-28 | Stefan Battlogg | Desmodromischer Ventiltrieb |
EP1672183A1 (de) * | 2004-12-14 | 2006-06-21 | JOH. WINKLHOFER & SÖHNE GmbH & Co KG | Schwenkhebel für einen zwangsgesteuerten Ventiltrieb |
DE102004029621B4 (de) * | 2004-06-18 | 2006-09-07 | Dr.Ing.H.C. F. Porsche Ag | Ventiltrieb für eine Brennkraftmaschine |
DE102005033653B3 (de) * | 2005-07-19 | 2006-11-30 | Dr.Ing.H.C. F. Porsche Ag | Zwangsgesteuerter Ventiltrieb für eine Brennkraftmaschine |
KR101288649B1 (ko) | 2011-04-18 | 2013-07-22 | 독터. 인제니어. 하.체. 에프. 포르쉐 악티엔게젤샤프트 | 상이한 캠 프로파일을 가진 슬라이딩 부품을 구비한 캠샤프트 |
CN103362587A (zh) * | 2013-07-30 | 2013-10-23 | 长城汽车股份有限公司 | 发动机及其可变气门升程装置的致动机构 |
DE102017205538A1 (de) * | 2017-03-31 | 2018-10-04 | Mahle International Gmbh | Ventiltrieb für eine Brennkraftmaschine |
DE102018221107B3 (de) * | 2018-12-06 | 2019-09-26 | Heidelberger Druckmaschinen Ag | Vorrichtung in einer Druckmaschine |
WO2020014722A1 (de) * | 2018-07-16 | 2020-01-23 | Avl List Gmbh | Variable ventiltriebvorrichtung |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015214837A1 (de) * | 2015-08-04 | 2017-02-09 | Zf Friedrichshafen Ag | Hydraulische Radialkolbenmaschine |
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DE3700715A1 (de) | 1986-01-22 | 1987-07-23 | Volkswagen Ag | Zwangssteuerung fuer ein ventil |
US5505168A (en) * | 1994-02-25 | 1996-04-09 | Osaka Fuji Kogyo Kabushiki Kaisha | Variable lift height valve driving device |
WO2001012958A1 (de) | 1999-08-12 | 2001-02-22 | Stefan Battlogg | Ventiltrieb, insbesondere für brennkraftmaschinen von kraftfahrzeugen |
FR2817908A1 (fr) | 2000-12-11 | 2002-06-14 | Peugeot Citroen Automobiles Sa | Dispositif de commande d'une soupape, et ensemble de controle de l'admission et de l'echappement comprenant un tel dispositif |
WO2003014535A1 (de) * | 2001-08-06 | 2003-02-20 | Stefan Battlogg | Vorrichtung zur umwandlung einer drehbewegung in eine hin- und hergehende bewegung |
-
2003
- 2003-02-17 WO PCT/AT2003/000050 patent/WO2003083269A1/de not_active Application Discontinuation
- 2003-02-17 DE DE20320710U patent/DE20320710U1/de not_active Expired - Lifetime
- 2003-02-17 AU AU2003208163A patent/AU2003208163A1/en not_active Abandoned
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
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DE3700715A1 (de) | 1986-01-22 | 1987-07-23 | Volkswagen Ag | Zwangssteuerung fuer ein ventil |
US5505168A (en) * | 1994-02-25 | 1996-04-09 | Osaka Fuji Kogyo Kabushiki Kaisha | Variable lift height valve driving device |
WO2001012958A1 (de) | 1999-08-12 | 2001-02-22 | Stefan Battlogg | Ventiltrieb, insbesondere für brennkraftmaschinen von kraftfahrzeugen |
WO2001012959A1 (de) | 1999-08-12 | 2001-02-22 | Stefan Battlogg | Ventiltrieb, insbesondere für brennkraftmaschinen |
FR2817908A1 (fr) | 2000-12-11 | 2002-06-14 | Peugeot Citroen Automobiles Sa | Dispositif de commande d'une soupape, et ensemble de controle de l'admission et de l'echappement comprenant un tel dispositif |
WO2003014535A1 (de) * | 2001-08-06 | 2003-02-20 | Stefan Battlogg | Vorrichtung zur umwandlung einer drehbewegung in eine hin- und hergehende bewegung |
Cited By (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1580405A1 (de) * | 2004-03-26 | 2005-09-28 | Stefan Battlogg | Desmodromischer Ventiltrieb |
EP1600610A2 (de) | 2004-05-29 | 2005-11-30 | Dr.Ing. h.c.F. Porsche Aktiengesellschaft | Ventiltrieb für eine Brennkraftmaschine |
DE102004026430B3 (de) * | 2004-05-29 | 2005-09-01 | Dr.Ing.H.C. F. Porsche Ag | Ventiltrieb für eine Brennkraftmaschine |
EP1600610A3 (de) * | 2004-05-29 | 2008-08-20 | Dr. Ing. h.c. F. Porsche Aktiengesellschaft | Ventiltrieb für eine Brennkraftmaschine |
EP1607588A3 (de) * | 2004-06-18 | 2008-08-20 | Dr. Ing. h.c. F. Porsche Aktiengesellschaft | Ventiltrieb für eine Brennkraftmaschine |
DE102004029621B4 (de) * | 2004-06-18 | 2006-09-07 | Dr.Ing.H.C. F. Porsche Ag | Ventiltrieb für eine Brennkraftmaschine |
EP1672183A1 (de) * | 2004-12-14 | 2006-06-21 | JOH. WINKLHOFER & SÖHNE GmbH & Co KG | Schwenkhebel für einen zwangsgesteuerten Ventiltrieb |
DE102005033653B3 (de) * | 2005-07-19 | 2006-11-30 | Dr.Ing.H.C. F. Porsche Ag | Zwangsgesteuerter Ventiltrieb für eine Brennkraftmaschine |
KR101288649B1 (ko) | 2011-04-18 | 2013-07-22 | 독터. 인제니어. 하.체. 에프. 포르쉐 악티엔게젤샤프트 | 상이한 캠 프로파일을 가진 슬라이딩 부품을 구비한 캠샤프트 |
CN103362587A (zh) * | 2013-07-30 | 2013-10-23 | 长城汽车股份有限公司 | 发动机及其可变气门升程装置的致动机构 |
DE102017205538A1 (de) * | 2017-03-31 | 2018-10-04 | Mahle International Gmbh | Ventiltrieb für eine Brennkraftmaschine |
US10641138B2 (en) | 2017-03-31 | 2020-05-05 | Mahle International Gmbh | Valve drive for an internal combustion engine |
WO2020014722A1 (de) * | 2018-07-16 | 2020-01-23 | Avl List Gmbh | Variable ventiltriebvorrichtung |
DE102018221107B3 (de) * | 2018-12-06 | 2019-09-26 | Heidelberger Druckmaschinen Ag | Vorrichtung in einer Druckmaschine |
Also Published As
Publication number | Publication date |
---|---|
AU2003208163A1 (en) | 2003-10-13 |
DE20320710U1 (de) | 2005-02-10 |
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