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WO1998045622A1 - Convertisseur et/ou transmetteur de couple - Google Patents

Convertisseur et/ou transmetteur de couple Download PDF

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Publication number
WO1998045622A1
WO1998045622A1 PCT/EP1998/002006 EP9802006W WO9845622A1 WO 1998045622 A1 WO1998045622 A1 WO 1998045622A1 EP 9802006 W EP9802006 W EP 9802006W WO 9845622 A1 WO9845622 A1 WO 9845622A1
Authority
WO
WIPO (PCT)
Prior art keywords
torque converter
shaft
converter according
torque
peripheral surface
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.)
Ceased
Application number
PCT/EP1998/002006
Other languages
German (de)
English (en)
Inventor
Bernd Volle
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of WO1998045622A1 publication Critical patent/WO1998045622A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H33/00—Gearings based on repeated accumulation and delivery of energy
    • F16H33/02—Rotary transmissions with mechanical accumulators, e.g. weights, springs, intermittently-connected flywheels
    • F16H33/04—Gearings for conveying rotary motion with variable velocity ratio, in which self-regulation is sought
    • F16H33/08—Gearings for conveying rotary motion with variable velocity ratio, in which self-regulation is sought based essentially on inertia
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/04—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type
    • F16D7/06—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with intermediate balls or rollers
    • F16D7/10—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with intermediate balls or rollers moving radially between engagement and disengagement

Definitions

  • the invention relates to a torque converter and / or transmitter having a rotatably mounted drive part which transmits the input torque and an output part which is acted upon by the output torque and in particular is rotatably mounted concentrically thereto.
  • Torque converters are known in a variety of designs that work according to different principles and have different structural designs. They are all more or less complicated and therefore expensive to set up. The energy transfer between the input shaft and the output shaft is often non-positive or by means of frictional forces.
  • An object of the present invention is to provide a torque converter and / or transducer in which the torque on the output side can be adjusted without interruption to Erköm union constructions and which, like conventional gear shift transmissions, has a high mechanical efficiency.
  • one of the two parts has at least one run-off element on ice, which is guided along a peripheral surface of the other part, while this base surface has regions with different radial distances from the axis, and d ß for torque transmission there at least one drain member is radially displaced by the action of the different axial spacings of the peripheral surface during the movement along the peripheral surface and / or radially displaceable regions of the peripheral surface are displaced radially by the action of the at least one drain member guided thereon.
  • the torque converter according to the invention is based on the principle that each time it passes through a region projecting towards the outlet member, which is preferably a bump-like area
  • Projection can be formed, by means of which the drainage element, which is designed in particular as a roller, deflects either the drainage element or the bump-like projection or both.
  • the drive part transmits a pulse to the driven part and thereby transmits a torque.
  • a new drive pulse is generated, which is based on the difference in the rotational speeds of the input and output shafts and the deflection of the Abi, i.e. the height of the hump, and the mass of the drain member depends.
  • the structural design can be made very simple and inexpensive, since only two concentrically rotatably arranged parts are required, one of which is provided with the graduations which are guided along the peripheral surface of the other part.
  • the peripheral surface preferably has protrusions protruding toward the flight circle of the at least one drain member.
  • Several Abi are preferably on each, in particular special two or four, arranged in a plane perpendicular to the axis evenly distributed over the circumference in order to increase the number of effective drive pulses per revolution.
  • the drainage elements which are designed as rotatably mounted rollers in particular, are in contact with the circumferential surface due to centrifugal force in most structural configurations, support of the system by spring force can be advantageous.
  • the drive part is designed as a drive shaft, on which the at least one outlet member is held radially outwardly by means of a telescopic or swivel lever-like holder by centrifugal force, the peripheral surface being the inner circumferential surface of the tubular driven part is.
  • the inner circumferential surface of the tubular driven part has at least one bump-like projection which can be changed in its radial distance from the axis of rotation of the drive shaft.
  • an actuator is advantageously used for the radial displacement of a pulse-receiving member which has at least one protuberance-like projection and which has a screw or sliding guide in the radial direction.
  • the pulse pick-up element expediently bears against the actuator and / or is toothed with the latter, if retraction without the action of drain elements is desired, an elastic shock absorber being arranged in particular between the pulse pick-up element and the actuator, if, due to the design of the torque converter in question, the discharge member experiences a discontinuity in the slope of its path when it reaches the cusp.
  • the actuator provided with a sliding guide for radial displacement at the radially outer end is guided on an inclined guide which is arranged on an adjusting device which can be displaced in the longitudinal direction of the axis of rotation.
  • the actuator provided with a screw guide has a drive wheel, in particular a bevel gear, which is connected in terms of drive to an adjusting device which is rotatably mounted concentrically to the axis of rotation of the drive shaft.
  • the transmitted torque can be changed continuously by moving or turning the adjusting device during operation.
  • two bump-like projections arranged at diametrically opposite locations on the tubular output tube form a pair of bumps, one or more pairs of bumps being able to be arranged distributed over the circumference.
  • a bistable so to say digital adjustment of the individual cusps or cusp pairs in the radial direction can occur, in particular an adjustment by means of an adjustment cylinder.
  • bumps of different heights and drainage members of different masses can be arranged distributed over the circumference and / or in the axial direction.
  • a further advantageous possibility for changing the transmitted torque is that several Abi Jerusalemgl i eder or Abi Jerusalem Gl i ederschreibe offset in the axial direction on the Drive shaft are arranged so that the inner circumferential surface of the driven part at one axial end region over the circumference has widely differing center distances and at the other axial end region over the circumference the same center distances, the center distances between the two end regions transitioning smoothly or stepwise into one another, and that means are provided for the axial displacement of the drive shaft relative to the driven part.
  • some or all of the Abi each reach areas with - based on the starting point - larger differences in the center distances, i.e. in areas with higher bumps, so that the transmitted torque increases, and with one Displacement in the opposite direction reduces the transmitted torque accordingly.
  • a further advantageous embodiment of the invention consists in that at least one holding part is provided which is radially displaceably mounted in the drive part or driven part and is provided with drainage members at its two end regions, at least one drainage member being guided along the inner circumferential surface of the tubular part that the other drain member is guided on a correspondingly spaced guide surface.
  • a first advantageous alternative is that the at least one holding part is mounted in a shaft, in particular a drive shaft, and that both discharge members of the at least one holding part rest against diametrically opposite points on the inner circumference of the tubular part, the distance between the two being opposite Make always constant over the scope. Due to this positive guidance, the drainage elements always rest on the tubular part, even in the non-rotating state.
  • the second alternative which has the same advantage, is that the at least one holding part is mounted in or on a hollow shaft, in particular a drive shaft, so that the radially outer one Drain member on the inner circumferential surface of the tubular part and the radially inner drain member is guided along an inner rotation part arranged inside the hollow shaft and rigidly connected to the outer tubular part, and that the distance between the contact points of the two Abi on each of the at least one holding part over the circumference, i.e. the entire rotation angle of 360, remains the same.
  • further Abi can be arranged on each pair in one plane.
  • a plurality of holding parts may in an advantageous manner for change of the transmitted torque in the axial direction offset to the hollow shaft mounted to be, wherein the inner peripheral surface of the tubular portion at an axial end portion 5 greatly different radial distances from the
  • Axis of rotation and at the other end region has the same center distances, the center distances between the two end regions transitioning smoothly or stepwise into one another, and wherein means for axially displacing the hollow shaft 0 relative to the tubular part are provided.
  • the drain members 5 designed as rollers for the stepless transition are advantageously provided with round shoulders at the axial end regions at those axial end regions which are inclined to those in the axial direction areas of the inner circumferential surface come into contact. This means that, despite the ° inclination, a larger contact surface can be achieved than with completely cylindrical rollers. If, on the other hand, a gradual change in the transmitted torque is desired, then a multi-stage transition of the center distances of the inner circumferential surface from an axial is expedient
  • Drain elements or pairs of drain elements are arranged at axial distances that correspond to the step spacings, wherein the axial displacement can be carried out in corresponding step increments.
  • the Abi aufgl i eder which are preferably designed as rollers, always lie over their entire width in stationary operation, with the exception of the end regions provided with rounded shoulders, on the step-like regions of the inner circumferential surface, so that less abrasion and less stress on the bearing are achieved can be.
  • the round shoulders of some drainage elements lie against the inclined transitions only during the displacement in the axial direction.
  • a digital, in particular bistable, adjustment of the bumps in the outer tubular part, in particular by means of adjusting cylinders, can also be carried out for this purpose.
  • a further advantageous embodiment of the invention is that a shaft encompassed concentrically by a hollow shaft forms the drive part and the driven part or vice versa, that on the inner circumference of the hollow shaft or on the outer circumference of the other shaft several Abi Jerusalem i eder at a fixed distance distributed over the circumference are arranged to the axis of rotation of the shafts, which are guided along the respective other shaft, and that this respective other shaft has a plurality of bump-like projections evenly distributed over the circumference, which, when passing through a respective drain member, towards or into this other shaft avoid centrifugal forces and / or springy or elastic.
  • Execution consists in that the drainage elements, which are preferably designed as rollers, can be stored at a fixed radial distance and only the protuberant projections have to be changed radially.
  • the number of Abi Jerusalemgl i eder formed as roles can be increased relatively easily.
  • the bump-like projections are arranged on pulse pick-up members, each of which is deflected by the action of the passing Abi Jerusalemgl i eder against the centrifugal forces and / or resilient and / or are designed to be elastic.
  • the pulse pick-up members can also be designed to be radially immovable and the rollers can run on them radially displaceably under spring pressure, the spring pressure being adjustable by means of actuators, in particular compressed air cylinders, for adjusting the transmitted torque.
  • Another advantageous constructive embodiment of the invention is that, in a modification of the described embodiments, instead of the radially displaceable or non-displaceable Abi on gl i eder and radially non-displaceable or relocatable areas of the counter surface axially displaceable or non-displaceable drain members and axially non-relocatable or Movable areas of annular surfaces occur which are oriented perpendicular to the axis of rotation and have bump-like projections in the axial direction.
  • the forces serving to transmit the momentum and torque have the direction of the axis of rotation, so that an additive superimposition with the centrifugal forces resulting from the rotational movement is avoided.
  • FIG. 1 shows a first embodiment of a torque converter with two telescopic rollers movable in the radial direction in a sectional view perpendicular to the axis of rotation
  • FIG. 1 shows the first exemplary embodiment shown in FIG. 1 in a sectional illustration perpendicular to the sectional plane of FIG. 1
  • Fig. 3 shows a second embodiment of a torque converter with two pivoting levers arti g in the radial direction displaceable rollers in a sectional view perpendicular to the axis of rotation
  • Fig. 4 shows a third embodiment of a torque converter with axially displaceable rollers for continuously changing the transmitted torque in a sectional view along the axis of rotation
  • 5 shows a fourth exemplary embodiment of a torque converter which represents a modification of the third exemplary embodiment shown in FIG. 4
  • FIG. 6 shows a fifth exemplary embodiment of a torque converter for the step-like adjustment of the transmitted torque in a sectional illustration along the axis of rotation
  • FIG sixth embodiment of a torque converter as a modification to the fifth embodiment shown in FIG. 6,
  • FIG. 8 shows a seventh exemplary embodiment of a torque converter with positively driven idler rollers in a sectional illustration perpendicular to the axis of rotation
  • FIG. 9 shows an eighth exemplary embodiment of a torque converter with a multiplicity of positively guided
  • FIG. 10 is a sectional view of the eighth exemplary embodiment shown in FIG. 9 transverse to the sectional plane of FIG. 9,
  • FIG. 11 shows a ninth exemplary embodiment of a torque converter with an adjusting device for bump-like projections on the rolling surface of the running rollers in a sectional representation transverse to the axis of rotation
  • FIG. 12 shows a tenth embodiment of a torque converter with an alternative embodiment an adjusting device for bump-like projections of the rolling surface in a sectional view along the axis of rotation
  • FIG. 13 shows an eleventh embodiment of a torque converter with radially immovable rollers in a sectional view transverse to the axis of rotation.
  • two telescopic guides 11 are fixed on opposite sides of a drive shaft 10 transmitting the input torque, e.g. by welding, on the end regions of which are displaceable in the radial direction, in each case one run-off roller 12 is rotatably mounted. These drain rollers 12 roll in the rotation of the
  • the run-off rollers 12 initially move, for example, along the regions of the inner peripheral surface
  • the telescopic guides 11 together with the run-off rollers 12 are displaced radially inward, since these run-off rollers 12 radially inward along an inwardly curved curve with the radius r be deflected.
  • This radius r is the radius of the rise curvature of the bump-like projections 16.
  • the radius r can change continuously in the case of non-circularly shaped rise edges.
  • the run-off rollers 12 are guided along the inner circumferential surface 14 by centrifugal force.
  • the telescopic guides 11 can also be equipped with compression springs 17, which support the contact of the drain rollers 12 on the inner peripheral surface 14. For the sake of simplicity, only one such compression spring 17 is shown.
  • drain rollers 12 in principle other Abi on each can be provided, e.g. Rollers or balls or sliding elements, such as sliding jaws, which slide along the lubricated inner peripheral surface 14.
  • rollers or balls or sliding elements such as sliding jaws, which slide along the lubricated inner peripheral surface 14.
  • cage guides can also be used instead of axis guides.
  • the principle of the torque converter according to the invention is based on a non-positive energy transmission between the drive part or the drive shaft 10 and the driven part 13. Frictional forces are not required for the energy transmission, although of course a certain amount of friction, which is undesirable here, always occurs .
  • the telescopic guides 11 for the radial displacement of the casters 12 are replaced by swivel lever arti ge brackets 18.
  • rigid levers 19 are fixed, for example welded, to the drive shaft 10 at opposite points, which extend in opposite radial directions.
  • pivoting levers 20 are pivotally mounted, which in turn have the rotatably mounted at their radially outer free end regions
  • Wear drain rollers 12 are guided along the rotation of the drive shaft 10 by centrifugal force on the inner circumferential surface 14 of the driven part 13.
  • the pivot lever arti gene brackets 18 can be dimensioned such that the pivot lever 20 and the lever elements 19 together form a straight line in the regions of the inner peripheral surface 14 with the radius r, that is to say are stretched o, or else the kink shown in FIG. 3 remains in to a certain extent also in the areas with the radius r.
  • 16 depressions can be formed in the driven part 13 in such a way that the pivot levers 20 can buckle in the opposite direction if, for example, the driven part 13 has a higher speed than the drive shaft 10 in the "push mode" .
  • These depressions can be omitted if, with the holder 18 extended and appropriately dimensioned, the drain rollers 12 are not in contact with the inner circumferential surface 14 with the
  • pivoting lever 20 is resiliently held on the inner circumferential surface 14, for example to support the centrifugal force effect and to also keep the system position on the inner circumferential surface when the torque converter is at a standstill to keep .
  • the third exemplary embodiment shown in FIG. 4 represents a modification of the second shown in FIG. 3
  • tubular driven part 21 In place of the very short tubular and rather ring-shaped driven part 13 according to the first two exemplary embodiments, there is a much longer tubular driven part 21, in which the radius r remains the same, but in which the height of the bump-like projections 16 from the left axial end region from to the right axial end region continuously decreases until the entire inner circumferential surface 14 has the radius r at the right axial end region.
  • the drive shaft 10 provided with the 3 o run-off rollers 12 is arranged to be axially displaceable, so that the run-off rollers 12 rotate depending on the axial displacement of the drive shaft 10 either in the area of large bump-like projections 16 or in the area of small bump-like projections 16. Since the drain rollers 12 roll in most axial positions on an inclination of the inner peripheral surface 14, the corresponding edge of the drain rollers 12 has a corresponding rounding 22 in order to enlarge the contact area between the drain rollers 12 and the inner peripheral surface 14.
  • the fourth exemplary embodiment shown in FIG. 5 represents a variant of the third exemplary embodiment with essentially the same function, that is to say that the transmitted torque can also be changed continuously by axially displacing the drive shaft 10 in the fourth exemplary embodiment.
  • the tubular driven part 21 with a cylindrical outer contour according to FIG. 4 is replaced by a tubular driven part 23, in which the outer diameter is increased to the left towards the regions with higher bump-like projections.
  • the mutually opposite surface lines of the inner circumferential surface 14 widen more and more towards the regions with higher projections 16, that is to say to the left, that is to say the radius r also increases from right to left.
  • the right area in which no torque is transmitted anyway, can be designed with a smaller diameter.
  • the run-off rollers 12 are rounded on the edge opposite to FIG. 4.
  • the exemplary embodiment shown in FIG. 5 can also be dimensioned in a modification such that the opposite generatrices in the upper region of the cusps narrow axially from right to left, while the opposite generatrices expand in the lower region of the cusps from right to left.
  • the boundary between the upper and lower area is formed by two cladding lines that run parallel to the drive axis.
  • the drain rollers 12 should be rounded on both edges.
  • a tubular driven part 24 is provided, in which the bump-like projections 16 increase from right to left in five stages 25, the number of stages being variable.
  • Each step has a cylindrical peripheral contour, so that the drain rollers 12 rest in their cylindrical area over their entire width on the Abiauffl surface.
  • a plurality of mutually opposed drain rollers 12 are arranged axially offset in stages and each held by pivoting lever arti ge brackets, as was already the case in the previous embodiments.
  • telescopic guides 11 according to the first embodiment can also be used here, and the number of bump-like projections 16 and run-off rollers 12 in one plane can be greater than two. In the illustrated embodiment, twelve pairs of rollers are axially offset on the drive shaft 10 so that the respective distance corresponds to the spacing of the steps 25.
  • the number of pairs of rollers in the area of the highest elevation of the protuberant projections 16 decreases, and accordingly the number of pairs of rollers in the cylindrical right inner region increases without torque transmission to five. This reduces the total torque transmitted.
  • the run-off rollers 12 also have curves on a running edge so that the inclined transitions between the stages can be used for the energy transfer during the shifting as in FIG. 4.
  • the sixth exemplary embodiment shown in FIG. 7 again largely corresponds in terms of function to the fifth exemplary embodiment shown in FIG. 6.
  • only three stages 26 are provided, and instead of the tubular driven part 24 there is a tubular driven part 27.
  • This tubular driven part 27 differs from the tubular driven part 24 in the same way as the driven part 23 according to FIG. 5 to the driven part 21 according to FIG. 4 except for the stages.
  • the run-off rollers 12 jump over the bump-like projections 16 in a jump-like manner, so that when they are relocated to the inner circumferential surface, the rising flank of the next bump is reached and a pral 1 effect occurs. which leads to noise pollution and increased wear.
  • the delayed placement can be reduced by additional springs, for example by the springs 17 according to FIG. 1, or else by leaf springs or the like. to the pivot lever arti gene mounts 18.
  • a disadvantage could be the appearance of resonance and a slightly increased energy loss due to heating of the springs in versions with springs.
  • Drain rollers 12 bypassed.
  • a rod-like or strip-like holding part 28 is mounted in a radially displaceable manner in a drive shaft 29 and runs through the axis of rotation of the drive shaft 29.
  • a run-off roller 12 is rotatably mounted on each of the two free ends of the holding part 28.
  • the guide of the holding part 28 in the drive shaft 29 must be secured against rotation, which is the case, for example, due to a non-circular cross section of the holding part 28, a guide strip or the like. is achieved.
  • the inner peripheral surface 30 of a tubular or annular driven part 31 is provided with bump-like projections 32 and depressions 33 that the diagonal distance d through the axis of rotation 15 is always constant and corresponds to the length of the holding part 28 provided with the run-off rollers 12. As a result, both drain rollers 12 are always positively guided along the inner circumferential surface 30.
  • FIG. 9 A modification of the seventh exemplary embodiment shown in FIG. 8, which is based on the same working principle, is shown in FIGS. 9 and 10. To simplify the illustration, FIG. 9 is only shown in part. In this embodiment, the run-off rollers 12 are also positively guided, and the transmitted torque can be changed in stages.
  • a drive shaft 34 designed as a hollow shaft has an extension designed as a guide tube 35, this guide tube 35 encompassing an output shaft 36 and being rotatably and axially displaceably mounted on it.
  • the output shaft 36 two concentric tubes 37, 38 are fixedly connected, the diameters of which are designed such that the drive shaft 34, which is designed as a hollow shaft, is arranged between them in the radial direction.
  • a plurality of axially offset pairs of discharge rollers 12 are mounted so as to be radially displaceable, each graduation on oil pairs being formed by two discharge rollers 12 which are held at the opposite ends of holding parts 39 which are radially displaceably mounted in the drive shaft 34 are rotatably mounted.
  • the basic functions of the holding parts 39 correspond to the holding part 28 of the seventh exemplary embodiment.
  • the total length of these pairs of rollers 40 corresponds to the radial distance between the surfaces on the concentric tubes 37, 38, so that a positive guidance is also achieved here.
  • a plurality of pairs of rollers 40 can also be arranged distributed over the circumference in each plane perpendicular to the axis of rotation 15, for example in pairs at diametrically opposite points.
  • the outer concentric tube 37 has bump-like projections 41 distributed over the circumference, which are highest at the right end region in FIG. 9 and whose height gradually decreases towards the left end region until that Concentric tube 37 has a cylindrical inner circumference at the left end region.
  • the inner concentric tube 38 In order to achieve the positive guidance of the pairs of rollers 40, the inner concentric tube 38 must have a complementary outer peripheral surface so that the radial distance to the positive guidance always remains constant.
  • the free end region of the drive shaft 34 is provided with two bearing rollers 42 in order to ensure reliable guidance of the drive shaft 34 between the tubes 37, 38 concentric there. 6 and 7, that is, the drive shaft 34 is gradually shifted axially, the number of pairs of rollers 40 increasing in the region of the bump-like projections 41 and in the one direction other direction is reduced. It is of course also possible, analogous to the exemplary embodiments according to FIGS. 4 and 5, to provide a continuously variable change instead of a step-like change in the height of the hump-like projections 41. In principle, the function of drive shaft and output shaft can also be interchanged in this exemplary embodiment.
  • the ninth exemplary embodiment shown in FIG. 11 in turn corresponds in principle to the second exemplary embodiment shown in FIG. 3.
  • the hump-like projections 43 of the pulse pick-up member 44 which can be pivoted about the axis 58, now occur.
  • This pulse pick-up member 44 is so deeply arranged in the inner wall of a tubular driven part 45 that the desired swivel adjuster 1 is possible.
  • the pulse pick-up member 44 rests on its side opposite the inner circumferential surface via an elastic shock absorber arrangement 46 on an actuator 47, which via a screw thread 48 in the wall of the driven part 45 about the axis 58, which in practice is left and right outside the raceway of the bump 43 must be attached, can be pivoted.
  • the transitions between the inner circumferential surface 14 and the pulse receiving member 44 should be as continuous as possible in order to avoid jumps of the run-off rollers 12.
  • the pulse pick-up member 44 can be made elastically deformable, so that the discontinuity of the path gradient at the transition between the inner circumferential surface 14 and the pulse pick-up member 44 disappears briefly when rolled over by the run-off roller 12 or at least does not come into play so strongly that the run-off roller jumps.
  • the pulse pick-up member 44 is rigid, the bump rising edge is expediently designed such that, as in FIG. 3, with the pulse pick-up member 44 fully swung out in the direction of the axis 15, there is no discontinuity in the path.
  • Impulse pickup member 44 are a little elastically deformable, jumping of the roller 12 can be almost completely avoided.
  • the pulse pickup member 44 can also be interlocked with the actuator 47 so that a retraction of the pulse pickup member 44 by means of the actuator 47 is possible.
  • the passing drain rollers 12 exert a force radially outwards.
  • the actuator 47 is provided at its radially outer end region with a bevel gear 49, which can be driven, for example, by means of a further bevel gear arranged concentrically with the drive shaft 10 and mounted thereon.
  • a bevel gear 49 which can be driven, for example, by means of a further bevel gear arranged concentrically with the drive shaft 10 and mounted thereon.
  • a modified embodiment of an actuator 50 is provided.
  • the actuator 50 coupled to the pulse pickup member 44 is slidably guided on a guide 51 which extends obliquely in the axial direction.
  • This guide 51 is rigidly connected via connecting disks 52, 53 to rotatably mounted pipe pieces 54 which are rotatably mounted on bearing pipes 55 connected to the tubular driven part 45.
  • the bearings 55 are in turn rotatably mounted on the drive shaft 10. Axial displacement of the pipe sections 54 or the connecting disks 52, 53 displaces the actuator 50 along the guide 51 and causes the pulse pickup member 44 to be radially adjusted.
  • a variety of setting options for the transmitted torque can be achieved by placing several independently adjustable pulse pick-up members next to each other not only over the circumference, but also in the axial direction, each of which is assigned an Abi on role arrangement, both of the cusp heights of each pulse pick-up member can be different as well as the masses of the assigned roles.
  • the respective adjustment between the two positions of the pulse pickup members 44 can be carried out, for example, by pneumatic, electrical or other actuators.
  • the holding devices 39 must have stop means in the hollow shaft 34 which limit the radial movement.
  • a drive shaft 56 is provided with an adjustable pulse pick-up. structure 44 similar to FIGS. 11 and 12.
  • Several such impulse pick-up members 44 are arranged distributed over the outer circumference of the drive shaft 56.
  • the drive shaft 56 is surrounded at a radial distance by a concentric output tube 57.
  • On its inner circumferential surface a plurality of run-off rollers 12 are rotatably mounted evenly over the circumference, but, in contrast to the previous exemplary embodiments, are not adjustable in the radial direction.
  • the angular distances between the drain rollers 12 correspond to the angular distances of the impulse pick-up elements 44. However, this need not be the case in every case.
  • the pulse receiving members 44 which are pivotably arranged on the drive shaft 56, are pivoted radially inward by the run-off rollers 12, and they then pivot radially outward again under the action of the centrifugal forces.
  • tangential force components occur again, which bring about the transmission of a torque.
  • drive shaft 56 and driven tube 57 can also be interchanged in the eleventh embodiment shown in FIG. 13; however, since then only slight centrifugal forces occur when the output shaft rotates slowly, the swiveling impulse receiving members should be pressed outwards with additional spring elements in this application.
  • the run-off rollers 12 can be arranged radially displaceably under spring pressure on the inside of the outer tube, while immovable or continuously or continuously on the inner shaft in the radial direction digitally adjustable bump-like projections 43 or pulse recording members 44 can be provided.
  • immovable bump-like projections these can then also have a changing height in the axial direction according to the exemplary embodiments shown in FIGS. 4 to 7, or the spring pressure can be adjusted by means of actuators, in particular compressed air cylinders, in order to have a step-like or continuous adjustability to achieve the transmitted torque.
  • drain rollers 12 In all exemplary embodiments with radially displaceable run-off rollers 12, these can be designed to be radially displaceable according to FIG. 1 or FIG. 3.
  • the number of drain rollers 12 in a plane perpendicular to the axis of rotation is in principle freely selectable, but arrangements are preferred in which drain rollers 12 face each other in pairs.
  • All of the torque converters described can also be made in several parts in such a way that several energy-transmitting units are positioned at different locations, both the drive parts and the output parts being non-positively, in particular non-rotatably, connected to one another.
  • these can also be implemented in such a way that instead of a radial displacement of discharge members and / or instead of radially displaceable regions of the counter-running surface, axially displaceable discharge members and / or axially displaceable regions of ring surfaces occur that are perpendicular are aligned with the axis of rotation.
  • This annular surface can have bump-like areas that extend in the axial direction extend, have for torque transmission, and the drain member can either rest resiliently or one of the two disc-like parts is axially displaceable on the axis of rotation and makes axial oscillating movements in the axial direction during the transmission of torque under axial spring pressure.
  • the drain member can either rest resiliently or one of the two disc-like parts is axially displaceable on the axis of rotation and makes axial oscillating movements in the axial direction during the transmission of torque under axial spring pressure.
  • Almost all of the exemplary embodiments described can also be used analogously for the axial displacement of the drain members and / or the rotatably mounted parts.
  • a holding part with Abi on Gl i edern at its two free ends in an input or output part can be axially displaceably and with its drain members arranged on both sides, rigidly with each other connected disc-like discharge or drive parts run out, which have axially extending bump-like projections which are arranged such that there are equally large distances in the axial direction everywhere between the surfaces serving as drainage surfaces, so that the holding part with its Abi Jerusalemgl i is subject to forced control.
  • either the axially displaceable holding part alone can perform oscillating movements in the axial direction relative to the central disk-like part, or it is attached to the central part in such a way that it cannot be displaced relative to the latter in the axial direction , so that the middle part follows the oscillating movements.
  • the adjustability of the abtri ebssei ti gene torque in the spring-mounted versions is realized in that the contact pressure of the Abi Jerusalemgl i eder individually or the axial distance between the two disc-like parts and thus the contact pressure of all Abi Jerusalemgl i eder can be adjusted.
  • a gradual adjustability of the torque on the output side can be realized in that several pairs of ring surfaces of the disc-like parts arranged to the left and right of the central part, depending on their distance from the axis, differ in axial distance
  • the holding part does not oscillate at all if it is between two ring surfaces without bumps, but between ring surfaces with bumps it oscillates with more or less high amplitude depending on the height of the bumps and the difference in the rotational speed of the middle part and the two side parts and frequency and thus determines the output side torque.
  • the middle part If the holding part is fixed in the middle part in such a way that it cannot move in the axial direction and can only be adjusted in the radial direction, the middle part as a whole oscillates relative to the side parts.
  • a gradual adjustability of the basically same arrangement can also be achieved in that for each pair of ring surfaces with the same radial distance from the axis, a fixed axial guide is arranged in the disc-like central part, in which there is an actuator, in particular a bistable compressed air cylinder, which a holding member located on the left of it in the guide can press to the left and a holding member located on the right can push to the right, so that the graduations rest on the left or right end of the respective holding part on the associated ring surfaces.
  • an actuator in particular a bistable compressed air cylinder
  • one of the pairs of holding parts is by means of the corresponding compressed air cylinder spread and locked so that the middle part or the two interconnected side parts oscillate when rotating and depending on the amplitude and frequency on the abtri ebssei ti ge torque accordingly influence.
  • Guides are arranged, which can be applied to the associated Abi surfaces by means of actuators, in particular in the end positions of lockable compressed air cylinders.
  • the middle part will oscillate with the amplitude relative to the side parts with a greater or lesser amplitude and thus reduce the output-side torque.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

L'invention concerne un convertisseur et/ou un transmetteur de couple comportant une partie entraînée (10) montée rotative transmettant le couple d'entrée, et une partie menée (13), montée rotative concentriquement à la partie entraînée (10), et à laquelle est appliqué le couple de sortie. L'une des deux parties possède un organe de positionnement (12) se présentant notamment sous la forme d'un galet de positionnement, qui est guidé le long d'une surface périphérique (14) de l'autre pièce (13), cette surface périphérique (14) comprenant des régions présentant différentes distances radiales par rapport à l'axe de rotation (15). Pour la transmission du couple, le ou les organes de positionnement (12) sont déplacés radialement par rapport à la surface périphérique (14) lors du mouvement le long de celle-ci, en raison des différents entr'axes. On obtient ainsi une transmission de couple et d'énergie ne s'effectuant pas par liaison de force, sans que soient absolument nécessaires des forces de friction à cet effet. Ces convertisseurs de couple autorisent, comme les transmissions hydrauliques, un réglage du couple côté mené, sans interruption de la transmission d'énergie et sans utilisation d'un accouplement, et présentent des rendements mécaniques qui peuvent être identiques ou supérieures à ceux des transmissions par engrenages.
PCT/EP1998/002006 1997-04-09 1998-04-07 Convertisseur et/ou transmetteur de couple Ceased WO1998045622A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1997114605 DE19714605A1 (de) 1997-04-09 1997-04-09 Drehmomentwandler und/oder -übertrager
DE19714605.8 1997-04-09

Publications (1)

Publication Number Publication Date
WO1998045622A1 true WO1998045622A1 (fr) 1998-10-15

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PCT/EP1998/002006 Ceased WO1998045622A1 (fr) 1997-04-09 1998-04-07 Convertisseur et/ou transmetteur de couple

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DE (1) DE19714605A1 (fr)
WO (1) WO1998045622A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10229751A1 (de) * 2002-07-03 2004-01-29 Künstler, Georg Fliehkraft Kupplungsanordnung
RU2531856C2 (ru) * 2013-02-12 2014-10-27 Геннадий Георгиевич Сосин Автоматический инерционный трансформатор
US9222523B2 (en) 2013-07-09 2015-12-29 Solarcity, Inc. Dual-mode torque transfer in laterally engaging drive couplers exhibiting axial misalignment with driven couplers
US9982722B2 (en) 2013-07-09 2018-05-29 Solarcity Corporation Torque transfer in laterally engaging drive couplers exhibiting axial misalignment with driven couplers
DE102023101771A1 (de) 2023-01-25 2024-07-25 Jochen Schleef Antriebsvorrichtung mit einem Grundkörper und mit mindestens einer Rotationseinheit

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006082191A1 (fr) * 2005-02-01 2006-08-10 Carsten Tegtmeyer Torque transmission device
DE102010017192A1 (de) * 2010-06-01 2011-12-01 Zack Gmbh Saughalterung

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Publication number Priority date Publication date Assignee Title
US2232234A (en) * 1939-01-31 1941-02-18 Perley A Hilliard Automatic variable speed power transmission mechanism
US2366637A (en) * 1941-09-24 1945-01-02 Mejean Jacques Gustave Transmission system
DE1074351B (de) * 1960-01-28 Maag-Zahnräder und -Maschinen Aktiengesellschaft, Zürich (Schweiz) Ausgleichgetriebe mit zwei gleichachsigen Schubkurvenkörpern
DE2703171A1 (de) * 1976-01-26 1977-07-28 Shea Inventive Designs Inc Drehmomentwechselkupplung

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US4336870A (en) * 1977-01-06 1982-06-29 Shea Inventive Designs Torque exchange coupling
DE3430812A1 (de) * 1984-08-22 1986-03-06 Ludwig 6732 Edenkoben Graeber Drehmomentwandler

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1074351B (de) * 1960-01-28 Maag-Zahnräder und -Maschinen Aktiengesellschaft, Zürich (Schweiz) Ausgleichgetriebe mit zwei gleichachsigen Schubkurvenkörpern
US2232234A (en) * 1939-01-31 1941-02-18 Perley A Hilliard Automatic variable speed power transmission mechanism
US2366637A (en) * 1941-09-24 1945-01-02 Mejean Jacques Gustave Transmission system
DE2703171A1 (de) * 1976-01-26 1977-07-28 Shea Inventive Designs Inc Drehmomentwechselkupplung

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10229751A1 (de) * 2002-07-03 2004-01-29 Künstler, Georg Fliehkraft Kupplungsanordnung
RU2531856C2 (ru) * 2013-02-12 2014-10-27 Геннадий Георгиевич Сосин Автоматический инерционный трансформатор
US9222523B2 (en) 2013-07-09 2015-12-29 Solarcity, Inc. Dual-mode torque transfer in laterally engaging drive couplers exhibiting axial misalignment with driven couplers
US9982722B2 (en) 2013-07-09 2018-05-29 Solarcity Corporation Torque transfer in laterally engaging drive couplers exhibiting axial misalignment with driven couplers
DE102023101771A1 (de) 2023-01-25 2024-07-25 Jochen Schleef Antriebsvorrichtung mit einem Grundkörper und mit mindestens einer Rotationseinheit

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