FR2602019A1 - DRAWING DEVICE FOR PLANETARY GEARS - Google Patents

Abstract

PLANETARY GEAR COVERING DEVICE DEPENDING ON THE DIRECTION OF ROTATION. A 5 CUNEIFORM OR SINGLE OR DOUBLE ANGLE FEEDER IS IN CONTACT WITH THE FLAT OR FRONT SIDES OF THE WHEELS 1, 2 OF THE GEAR FOR THE GEAR. THE SHIFTING IS PROVIDED BY A CONTROL ELEMENT 8 TURNING IN RELATION TO THE PRIMARY DRIVE 10 AND INCLUDING CLAWS 9, 9, MOBILE OR RIGID, WHICH ACT ON THE FEEDER AND THE PRIMARY DRIVE. THE INVENTION IS ADVANTAGEALLY APPLICABLE TO SMALL LIFTING DEVICES.

Description

The present invention relates to a skidding device that can be used in

  planetary gears for their clutch depending on the direction of rotation. It is advantageously usable in

small lifting devices.

  German Offenlegungsschrift 2,658,158 discloses a brake for hoisting apparatus, the axially movable brake discs of which, by means of a rapid step, are brought to a driving shaft by force action, a freewheel of the type conventional, locking in the direction of rotation, being used for the transmission of the braking torque. Commercial hoisting devices currently use load-driven screw brakes, each in the form of a separate module which, by means of a fast pitch, displaces axial brake disks on the gearbox primary shaft in order to produce an axial force action. The action of force is produced by a pawl which, connected to the body of the apparatus, prevents the rotation of an axial brake disc to be disengaged according to the direction of rotation and thus produces an axial translation by the primary shaft threaded. The two braking devices shown here as examples of multiple similar solutions have the disadvantage of not being part of the gearbox, but of being modules acting solely by force action and arranged upstream of the gearbox. Torque dependent action is not possible with a separate braking unit. Neither the kinematics nor the internal efficiency of the gearbox are used to produce or maintain the clutch. The brakes must carry all the resistant torque. As a result of their realization in the form of separate modules, the braking devices constituted by many spare parts represent a high investment in materials and manufacturing; however, they are also subject in use to external influences, which represent disadvantages for the operability, the safety of

  operation and maintenance. These solutions are not applicable as overload protections.

  The object of the invention is to provide a skidding device representing a reduced investment in materials and workmanship, requiring only reduced maintenance, without disturbing the ability to function properly.

  safety, and usable as overload protection.

  The subject of the invention is a planetary gearing device for planetary gears, of simple constitution, using gearbox kinematics as a parameter determining the automatic production of the gearing with influence of the efficiency of the gearbox when stopped, which can be used as protection against overloads and submitted only

  to the environmental conditions inside the gearbox.

  According to an essential characteristic of the invention, a wedge-shaped or single or double-angle scraper is in contact with the

  flat or front surfaces of the wheels of the gear; and a control element rotating relative to the primary drive comprises rigid or movable cleats which act on the framer and the primary drive.

  In a skidding device according to the invention, particularly suitable for oscillating wheel gears acting in space, the skirmisher made in the form of a single or double angle acts by its radial branches on the flat faces of the oscillating wheel and / or fixed wheel and its axial branch is connected to the primary entrainment by a movable force action. The radial branch

  of a single angle-then engages in a radial groove of the oscillating wheel or between the rear planar face of the fixed wheel and the bearing of the primary drive.

  In one embodiment of the invention, the radial branch 25 comprises a guide pin which penetrates into the radial groove of the

  oscillating wheel and acts on the bearing of the oscillating wheel.

  In the case of a wedge-shaped and crampon-shaped scraper with two radial branches, a limb acts either on the flat faces of the radial groove of the oscillating wheel or on the rear plane face of the oscillating wheel, while other branch is

  in contact with the flat rear face of the fixed wheel.

  The radial branches may be made symmetrically or otherwise with respect to the meshing point of the wheels of the gear and

  have central notches.

  Rectangular, triangular or circular profiles,

  caves or convexes, are provided for the section of the throat of the wheel ocillante and parts of the radial branch penetrating into said groove.

  The axial white of the fright is either straight or bent. A straight leg engages in a notch in the planar face of the primary drive and an axial limb bent in a notch in the envelope surface of the primary drive.

  According to the invention, the radial branches may also include a notch into which a cleat of the control element engages.

  The control element can according to the invention have two cleats acting on the outer end faces of the framer or penetrating into notches of the primary drive. These cleats are either integral with the primary drive or the control element, or rotatably mounted on the control element or mobile

axially under prestressing.

  In another variant of the fright, a washer

  stop is disposed between its radial branch and the bearing of the primary drive or the oscillating wheel.

  When applying a rotational movement or a torque to the control element of the primary drive of the gear in the direction of rotation constituting the direction of operation of the latter, for which a reduction of The efficiency of the gearing is unacceptable, the skidding device particularly suitable for an oscillating wheel gear rotates, by its framer in the form of a single or double angle, the control element on the primary drive. so that the cleat following the radial branch of the framer in the direction of rotation causes said framer to a position which excludes the force action with the oscillating wheel. The cleat simultaneously drives in the direction of rotation the primary drive by its notch. This state is maintained as long as a torque is exerted on the control element. The gear

  then works without reducing its performance and is not stopped.

  When the control element or the primary drive is not driven and a torque is exerted on the driven shaft, the oscillating wheel

  The printer imparts a rotational movement to the primary drive of the gear, the speed of which is the product of the rotational speed of the driven shaft and the ratio of the gear. The oscillating wheel presents the rotational speed of the driven shaft. As a result of the higher rotational speed of the primary drive, the framer is actuated through its axial leg, so that the radial branch tilts and produces a force action between the framer and the oscillating wheel by lateral contact of its flanks with the flat face of the oscillating wheel. The friction moment thus produced, acting in the direction opposite to the direction of rotation of the primary drive, influences the efficiency of the gear at standstill to the point that the total efficiency of the gear reaches the area of the drive. autoenrayage. Closing is facilitated by a couple of

  overturning such that the reversing directions of the oscillating wheel 15 and the framer are opposite.

  When an additional torque is applied to the control element in the direction of clutching of the gear, opposite to the direction of operation, the control element rotates on the primary drive so that the cleat following the radial branch the framer 20 in the direction of rotation again moves the framer to partially or completely remove the force action between the framer and the oscillating wheel. The gear then has a yield that no longer guarantees the self-clutch and the motor torque prints a movement to the primary drive. As a result of the different angular velocity of the control element or the primary drive and the oscillating wheel, as well as the higher rotational speed of the primary drive, permanent control of the braking force is obtained. performs with a clutch that the control element-can however permanently remove too; the primary drive continuously drives the rotational movement of the control element, produced from the outside. The realization of the rotational movement is facilitated by the engagement of the cleat of the control element in a notch of the primary drive. The absolute clutching torque must therefore not be overcome for driving the control element and

  primary training in the opposite direction to the sense of

2602019 9

gearing.

  In the embodiment with a wedge-shaped scraper, the two radial branches of which act as a crampon on the radial faces of the oscillating wheel-fixed wheel pair, the cleat in the form of a crampon drives the crampon at the speed angle of the primary drive when applying a torque to the control element in the direction of operation of the gear, so that there is no force-action contact between the fright, the fixed wheel and the oscillating wheel; the gear is not jammed and operates at its maximum efficiency. When no torque is applied to the control element and the motor shaft is loaded by a torque, the control element and the primary drive have no influence on the framer. The torque exerted on the driven shaft, however, produces a rotational movement of the primary drive via the oscillating wheel. The framer being force-connected to the oscillating wheel and the fixed wheel, and a rotation of the oscillating wheel being only possible by its superimposed overturning movement, the clutching action of the framer does not produce a rotational movement of the primary drive with the control element as a result of prohibiting the overturning of the oscillating wheel with respect to the fixed wheel; the gear is stopped. A total or partial suppression of the clutch is carried out in the same way as in the embodiment with a fright

in single or double angle.

  Other features and advantages of the invention will be

  better understood from the following detailed description of several exemplary embodiments and the accompanying drawings in which: Figure 1 shows schematically the mounting of a framer with a single radial branch and a control element in a engre30 swimming oscillating wheel and driving drum;

  Figure 2 is the section A-A according to Figure 1; Figure 3 is the view x according to Figure 1, with the framing in the direction of operation of the gear; FIG. 4 is the view x according to FIG. 1 with a clutch in the direction of clutching the gear;

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  Fig. 5 shows the mounting of a radial two-spoke framer and control member in an oscillating wheel gear and drive drum; Figure 6 is the section c-C according to Figure 5; Figure 7 is the view Z according to Figure 5 with framer in the direction of operation of the gear; Figure 8 is the view Z according to Figure 5 with the clutch in the direction of clutching the gear; Figure 9 shows a framer with a symmetrical radial branch; Figure 10 is the side elevation according to Figure 9; Figure 11 shows a framer with an asymmetrical radial branch; Figure 12 is the side elevation according to Figure 11; FIG. 13 represents a framer with an asymmetrical radial branch and an angled axial branch; Figure 14 is the side elevation according to Figure 13; FIG. 15 represents the bravery-groove shape safety profile of the oscillating wheel with concave-convex rectangular faces; FIG. 16 represents the bravery-shaped shape safety profile of the oscillating wheel with concave-convex triangular faces; FIG. 17 represents the shape safety profile of the oscillating wheel with concave-convex circular faces; Figure 18 is the plane of a pair of fixed wheel-oscillating wheel with a framer with two radial branches; Fig. 19 is the D-D section according to Fig. 18 with groove in the oscillating wheel; Figure 20 is the D-D section of Figure 18 without a groove in the oscillating wheel; Figure 21 is the plane of a pair of fixed wheel-oscillating wheel with two asymmetrical radial branches; Fig. 22 shows the mounting of a framer to a radial branch to influence the efficiency of the primary drum-drive bearing; Fig. 23 shows the mounting of a framer to a radial branch to influence the efficiency of the oscillating wheel bearing; Fig. 24 is the view W according to Fig. 22; Figure 25 is the view V according to Figure 23; Fig. 26 shows the block diagram with rigid tabs without abdication of Fig. 27 shows the block diagram with rigid tabs with application of one of the operation of the gear; Figure 28 shows the block diagram with rigid cleats with application of a clutch gear; Figure 29 shows the block diagram with mobile cleats with application of gear operation; Fig. 30 shows the block diagram of the comcouple element; of the comcouple element in the direction of the comcouple element in the direction of a comcouple element in the direction of a movable lug control element with application of a torque in the operating direction of the gear; Fig. 31 shows the block diagram of the control element at a rigid cleat without applying a torque; Fig. 32 shows the block diagram of the rigid lug control member with application of a torque in the direction of operation of the gear; and Fig. 33 shows the block diagram of the control element with a rigid cleat with application of torque in the direction

clutching the gear.

  FIGS. 1 to 4 show schematically a planetary gear in the form of an oscillating wheel gear of known type, with a fixed wheel 2 on which an oscillating wheel 1 rolls in space, driven by a primary drive constituted by a drum of 10. The constant velocity joint 4 ensures the transmission to the driven shaft 12. The oscillating wheel 1 comprises a radial groove 3 into which the radial arm 7 of the framer 5 provided in the form of a single bracket, penetrates. that the axial branch 6 of the framer 5 is connected by safety of form but with a defined clearance to the primary drive 10. A control element 8 provided with cleats 9, 9 ', serving for the application of the engine torque Man , Rotates freely on the primary drive 10, over the allowable travel range ES.Application of a torque Man to the control element 8 rotates the latter on the primary drive 10 to a position o of a p The cleat 9 'brings the framer into a position where force contact with the groove 3 of the oscillating wheel 1 is excluded and the primary drive 10 is driven in the same direction; on the other hand, when the force action is established between the framer 5 and the groove 3 of the oscillating wheel 1 by the cleat 9, the framer is brought into a position where the force action is removed until to a size for which there is no longer jamming. The primary drive is driven simultaneously in the same direction as a result of the contact of the cleat 9 with a notch 21 of said drive. As a result of its free rotation on the primary drive 10, the control element 8 rotates relative to the primary drive 10 when the skidding limit is reached, until the stoppage is restored as a result of a greater force action between the framer 5 and the groove 3 of the oscillating wheel 1. This alternation repeats continuously as a torque Man is applied to the control element 8 in the opposite direction to the operating direction of the gear. The motor torque Man in this direction is thus less than the clutching torque. In the absence of drive of the control element 8, there is generally clutching because the motor torque Mab produces a force action of full amplitude

  between the framer 5 and the groove 3 of the oscillating wheel 1. The control element 8 is then in an unstable state of rotation on the primary drive 10 because it is not loaded.

  Figure 3 shows the position of the frog 5 in the throat

  3 of the oscillating wheel 1 and in the primary drive 10 for the direction of operation of the gear at the maximum possible yield.

  The angular velocity w1 of the primary drive 10, a function of the ratio, is greater than the angular velocity w2 of the oscillating wheel 1. The primary drive 10 passes the oscillating wheel 1.

  The framer 5 rotates around the primary drive 10 at the angular velocity w1. The radial branch 7 of the framer is guided by safety in shape in the groove 3 of the oscillating wheel 1, the axial branch 6 is connected by safety of form to the primary drive 10. The cleat 9 'of the element control 8 abuts on the indentation of the primary drive 10 and simultaneously on the radial branch 7 of the framer 5 and simultaneously drives the two parts in the w1 direction. The cleat 9 is at the distance EAS of the framer 5, so that a contact is excluded. The control element 8 with the cleats 9, 9 'and the primary drive 10 rotating simultaneously at the angular velocity w1, the radial branch 7 of the framer 5 is parallel to the flat faces of the groove 3 of the oscillating wheel T and there is no force action between the frost 5 and the groove 3; There's no

  jamming. The axial branch 6 of the framer 5 is then perpendicular to the groove 3 of the oscillating wheel 1 and actuated by the primary drive 10.

  FIG. 4 shows the position of the framer 5 in the groove 3 of the oscillating wheel and in the primary drive 10 for the direction of clutching of the gear. The driven shaft 12 is loaded by a torque Mab transmitted by the constant velocity joint 4 to the oscillating wheel 1. The rotation of the oscillating wheel 1 at the angular velocity w2 can then be effected only by a superimposed reversal of the wheel 1 in the direction KT, the primary drive 10 with the control element 8 being then rotated at the angular velocity wl 'The control element 8 with its lugs 9, 9' is not loaded by a torque and is in an unstable rotational state on the primary drive 10; the cleats 9, 9 'do not act on the framer 5. As a result of its angular velocity w1 greater than w2, the primary entrainment 10 exceeds the oscillating wheel 1 and actuates the axial branch 6 of the framer 5 of so that the radial branch 7 of the framer 5 is connected by force action to the groove 3 of the oscillating wheel 1 and thus produces a clutching torque acting in the. opposite direction to that of the angular velocity w2 of the oscillating wheel 1. This results in a clutch of the primary friction drive, the intensity of which can be determined according to the ratio of the lever arms a and 1 of the 5. The meaning of

  reversal KT of the oscillating wheel 1 being opposed to the reversal direction KP of the framer 5 and a rotation of the oscillating wheel 35 1 at the angular velocity w2 can only be produced by a return

2602 0 1 9

  superimposed delivery of the oscillating wheel 1 in the direction KT, the reversal in the opposite direction of the oscillating wheel 1 and the framer 5 also produces a reaction torque which is related to the rotation of the primary drive 10 and the oscillating wheel 1 caused by the torque Mab. The clutch is thus obtained by a frictionally produced torque stabilized by a geometrically produced reaction torque. When a torque Man is applied to the control element 8 in the direction of clutching of the gear, this element 8 rotates on the primary drive 10 until the cleat 9 of the gear 5 removes in the direction w2 the force-acting connection with the groove 3 of the oscillating wheel 1. As a result of the torque Mab on the driven shaft 12, the primary drive 10 rotates again at the angular speed 1 until the absolute stopping state is reached again. This cycle is constantly repeated as long as a

  Man torque is applied to the control element 8 in the direction of clutching the gear. The driving torque Man applied to the control element 8 in the direction of clutching the gear is thus determined by the clearance forces of the framer 5 and the intensity of the absolute clutching torque is not used for movement.

  FIGS. 5 to 6 show schematically an oscillating wheel gear with a clutch device whose crampon-shaped clutch 5 comprises two radial branches 7, 7 ', the branch 7' being disposed on the rear plane face of the fixed wheel 2 and the branch 7 in the groove 3 of the oscillating wheel 1. The motor torque Man in the direction of operation of the gear is applied via the control element 8 with its cleats 9, 9 and transmitted by the primary drive 10 to the oscillating wheel 1. The stenter 5 is not actuated here by the primary drive 10 to produce a stopping torque, but the stopping is essentially obtained by the prohibition by safety of form of the overturning of the oscillating wheel 1 with respect to the fixed wheel 2, as a result of the contact of the branch 7 'with the flat face of the fixed wheel 2 and the

  branch 7 with the flat face of the groove 3 of the oscillating wheel 1. 35 The two radial branches 7, 7 'of the framer 5 are solid.

  FIG. 7 represents the view Z according to FIG. 5, in the form of development of the fixed wheel 2, the oscillating wheel 1 and the framer 5; the latter is in the position necessary for the direction of operation of the gear and in which there is no jamming. The cleat 9 of the control element 8 keeps the framer 5 in a position prohibiting a connection by force action and safety of form between the radial branches 7, 7 ', the fixed wheel 2 and the groove 3 of the oscillating wheel 1. The framer 5, the control element 8 and the primary drive 10 have the same angular velocity w1 '. FIG. 8 shows the view Z according to FIG. 5, in the form of the development of the fixed wheel 2, the oscillating wheel 1 and the framer 5 in the position necessary for the direction of clutching of the gear. The angular velocity of the framer 5 is w1 = 0 when no motor torque Man is applied to the control element 8. However, a resisting torque Mab is exerted on the driven shaft 12 and thus producing a rotation in the opposite direction to the gearing via the constant velocity joint 4 and the primary drive 10, a rotation of the oscillating wheel 1 at the angular velocity w2 is converted by a reversal of the oscillating wheel 1. The angular velocity w1 of the framer 5 being zero, a contact is established between the radial branch 7 'and the flat face of the fixed wheel 2, and between the

  radial branch 7 and the flat face of the groove 3 of the oscillating wheel 1, so as to exclude a new reversal of the oscillating wheel 1; the movement of the gear can not continue.

  Only the application of a torque Man to the control element 8 in the direction of clutching of the gear rotates said element on the primary drive 10 of a stroke ZSAS, so that the cleat 9 'deletes the connection by force action between the framer 5, the fixed wheel 2 and the oscillating wheel 1. The resisting torque Mab produces a new reversal of the oscillating wheel 1 until the establishment of a new contact between the oscillating wheel 1, the fixed wheel 2 and the radial branches 7, 7 'of the framer.5. This cycle repeats itself continuously as long as a motor torque -Man is applied to the control element 8 in the direction of clutching of the gear. Only the clearance forces, but not the absolute stop torque, are

  needed to overcome clogging.

  FIGS. 9 and 10 represent a possible form of the simple framer with a radial branch 7. The radial branch 7 of the framer 5 is symmetrical with respect to the center of the axial branch 6 and necessary in particular when the same action of clutch is required in both directions of rotation of the gear, without the application of a

  motor torque Man at the control element 8. The axial branch 6 of the shield 5 is straight and actuated by the lateral face of the primary entrainment 10.

  FIGS. 11 and 12 show another form of the framer with a radial branch 7. The radial branch 7 of the framer 5 is asymmetrical with respect to the center of the axial branch 6 and can be used when clutching in the direction of Gear clutching is a top priority, even when driving the control element. The axial branch 6 of the framer 5 is straight and actuated

  by the side face of the primary drive 10.

  Figures 13 and 14 show a fringe 5 at a branch

  radial 7 and whose axial leg 6 is bent so as to be actuated by the envelope surface of the primary drive 10.

  FIG. 15 represents a pairing of the rectangular section profiles of the radial branch 7 of the framer 5 and the groove 3 of the oscillating wheel 1. The clutching torque essentially results from the linkage by force action produced. by the lateral contact between the planar faces of the radial branch 7 and the groove 3 of the oscillating wheel 1. The clutching force is the friction force resulting from the ratio of the lever arms a and 1 of the framer 5 and the driving force exerted by the primary drive 10 on the axial limb 6. There are no radial reaction forces on the primary drive 10 in this case. The profile of the section of the radial branch 7 may be convex or concave and the

of the throat 3 concave or convex.

  According to FIG. 16, the section profiles of the radial branch 7 of the framer 5 and the groove 3 of the oscillating wheel 1 are triangular. The clutching torque essentially results from the force-acting connection produced by lateral contact between the inclined faces of the radial branch 7 and the groove 3, the friction force being produced by a resultant force of the control force. due to the contact of the primary drive 10 and the axial branch 6, the ratio of the lever arms a and 1 of the framer 5 and the angle of the profile of the branch 7 and the groove 3. The conditions of strength are those of a point; the effective friction force is increased. Losses due to mutual displacement and friction are excluded because the primary drive 10 and the framer 5 10 have the same angular velocity w1. The sectional profile of the radial branch 7 can be concave or convex and that of the throat

  3 in the convex or concave oscillating wheel 1. According to FIG. 17, the section profiles of the groove 3 in

  the oscillating wheel 1 and the radial branch 7 are circular.

  The functional conditions of the framer 5 and the groove 3 of the oscillating wheel 1, described above in the case of the triangular profiles, are transposable to the pairing of circular profiles, a differentiation of the friction force can be obtained as a result of the contact tangent resulting from the instantaneous lateral position of the radial branch 7 with respect to the groove 3. The sectional profile of the radial branch 7 may be convex or concave

  and that of the throat 3 concave or convex.

  FIG. 19 represents a framer 5 with two radial branches 7, 7 ', the radial branch 7' bearing on the rear planar face 25 of the fixed wheel 2 and the radial branch 7 in the groove 3 of the wheel

oscillating 1.

  FIG. 20 represents a skirt 5 with two radial branches 7, 7 ', the radial branch 7' bearing on the rear plane face of the fixed wheel 2, parallel to the toothing, and the radial branch 7 30 on the rear plane face. of the oscillating wheel 1. This assembly makes

  unnecessary additional throat 3 in the oscillating wheel 1.

  Figure 18 shows a framer 5 with two radial branches 7, 7 'symmetrical with respect to the axis. of the gear. This embodiment is necessary when a clutch is required for the two directions of rotation of the gear without motor torque Man on the control element 8 or the primary drive 10. The overturning prohibition of the oscillating wheel 1 relative to the fixed wheel 2 being advantageously effected on the outer points of the guard 5 as a result of the connection by safety of form and action of force, the central part of the radial branches 7, 7 'is indented, the accuracy of necessary production being limited to the outer points of the branches 7, 7 '. Figure 21 shows a framer 5 with two radial branches 7, 7 ', asymmetrical with respect to the axis of the gear. This embodiment is useful when an absolute clutch function of the direction is required for the direction of clutching of the gear without torque.

  Man on control element 8 or primary drive 10.

  According to FIGS. 22 and 24, the radial arm 7 of the wiper is arranged to move in a symmetrical manner with a defined clearance in a groove 3, the lateral faces of which are formed by the rear flat face of the wheel fixed 2 on the one hand and by a thrust washer 16appliqué on the bearing 14 of the primary drive on the other hand. The axial branch 6 of the framer 5 is bent and actuated by the casing of the primary drive 10. The application of a rotational movement to the primary drive rotates the framer-5 so as to apply the lateral faces of the radial branch 7 on the flat face of the fixed wheel 2 on the one hand and on the pressure washer 16 on the other hand. The thrust washer 16 thus produces a force-acting connection with the bearing rings 14 of the primary drive, rotating at different speeds, and thus reduces its efficiency.

  The force-acting connection is established by the contact of the radial branch 7 with the rear plane face of the fixed wheel 2. The control element 8, not shown, can suppress the clutch in the manner previously described.

  FIGS. 23 and 25 show a scraper 5 whose radial arm 7 is provided with a guide pin 17 rotating in the groove 3 of the oscillating wheel 1 and whose inner end of the arm acts on an abutment washer 16 applied to the wheel 15 of the oscillating wheel. The axial branch 6 of the fright 5

  is actuated by the lateral face of the primary drive 10.

  The application of a rotational movement to the primary drive rotates the framer 5 so that the guide pin 17 bears on the lateral faces of the groove 3 and consequently applies the thrust washer 16 to the bearing 15 of the oscillating wheel. The thrust washer 16 thus establishes a link by force action with the rings of the bearing 15 of the oscillating wheel, rotating at different speeds, and reduces its efficiency. Another linkage by force action results from the contact of the lug 10. 17 with the lateral faces of the groove 3. A control element 8 can eliminate the clutch in the manner previously described. FIG. 26 shows the mounting of a control element 8 with rigid cleats 9, 9 'in the case where the framer 5 is in the disengaged state and no motor torque is applied to the element 8. The cleats 9, 9 'are not in contact with the framer 5, the control element 8 is in a state of rotation

  unstable on the primary drive 10. The rotation of the primary drive 10 and the control element 8 is prohibited.

  Figure 31 shows the position of the control element 8 with rigid lugs 9, 9 'for the direction of operation of the gear. A motor torque + Man applied to the control element 8 rotates it on the primary drive 10 so that the cleat 9 'brings the radial branch 7 of the framer 5 in a position parallel to the groove 3 of the wheel oscillating 1 and drives

  the primary drive 10 in the same direction through the notch 21.

  A connection by force action between the framer 5 and the groove 3 is thus avoided and the clutch excluded as the control element

is charged by a couple.

  Figure 28 shows the position of the control element

  8 rigid cleats 9, 9 'for the direction of clutching the gear.

  A motor torque -Man applied to the control element 8 actuates the cleat 9 of the framer 5 being in the clutching position so that the inclination of its radial branch 7 in the groove 3 is removed until a position where the efficiency of the gear exceeds the self-clutch limit. The primary drive 10 is driven simultaneously in the same direction of rotation by the notch 21. The skirmisher 5 is thus partially released from the state of clutching and only part of the absolute clutching torque must be exceeded to the displacements of the primary drive 10 with the control element 8. FIG. 29 represents a control element 8 whose cleats 9, 9 'are movable in a hinge 19 and prestressed by elastic elements 20, so that it There is no folding of the cleats 9, 9 'to a defined torque on the primary drive 10. This state is advantageously that of the displacement of the primary drive 10 with the control element 8 in the direction of operation of the gear. The joints 19 of the catches 9, 9 'are connected to the control element 8. The movable catches 9, 9' can also be produced in the form of linearly moving snap parts. A driving torque + Man applied to the control element 8 rotates the latter on the primary drive 10 so that the cleat 9 'brings the radial branch 7

  5 in a position parallel to the groove 3 and causes in the same direction the primary drive 10 by the notch 21.

  A linkage by force action is thus avoided between the framer and the groove 3 of the oscillating wheel 1 and the clutch is excluded. Fig. 30 shows the movable cleat control element 8, 9 'in the state for which the motor torque on the control element 8 exceeds the permissible value. The tire of the elastic elements 20 adapted to a limit torque is exceeded; the cleats 9, 9 'fall back on the notch 21 of the primary drive 10 and slide on its envelope when the control element 8 continues its rotation. Rotation of the control element 8 in the direction of clutching of the gear closes the cleats 9, 9 'in their initial position as a result of the tire of the elastic elements 20. The control element 8 thus simultaneously assumes the

  function of overload protection.

  According to FIG. 31, the control element 8 comprises a single

  cleat 9 which engages in a notch 22 of the framer.

  8 is not loaded by a torque and is in an unstable rotational state on the primary drive 10. The cleat 9 may be rigid and wet. The fright 5 is in

the state of clutching.

  FIG. 32 shows the control element 8 in the operating direction of the gear, a torque + Man being applied to said element 8. Via the lateral face of the notch 22 located along the direction of rotation, cleat 9 brings fright 5

  in a position relative to the oscillating wheel 1 prohibiting a linkage by force action.

  Fig. 33 shows the control element 8 in the direction

  for clutching the gear, a pair -Man loading said element 8.

  The framer 5 is disengaged from its clutching position on the oscillating wheel by the cleat 9 which pulls the framer 5 by the lateral face 15 of the notch 22 located in the direction of rotation.

  Of course, various modifications may be made by those skilled in the art to the principle and to the devices which have just been described solely by way of nonlimiting examples, without

depart from the scope of the invention.

Claims (18)

claims   1. Clutching device for planetary gears, and in particular for oscillating wheel gears, characterized in that a cuneiform and c-shaped or single or double-angle scraper (5) is in contact with the planar faces or front wheels (1, 2) of the gear ratio determining; and a control element (8) rotating relative to the primary drive (10) comprises rigid or movable cleats (9, 9 'which act   on the framer (5) and the primary drive (10).   2. Clutch device according to claim 1, characterized in that the framer (5) formed as a single or double lever acts by its radial branches (7, 7 ') on the flat faces of the oscillating wheel ( 1) and / or the fixed wheel (2) and has a   movable form safety connection of its axial limb (6) with the primary drive (10).   3. Clutch device according to claims 1 and 2, characterized in that the radial branch (7) of the framer (5) enters a   radial groove (3) of the oscillating wheel (1).   4. Clutch device according to claims 1 and 2, characterized in that the radial branch (7) of the framer (5) acts between the   flat rear face of the fixed wheel (2) and the bearing (14) of primary training.   5. Clutch device according to claims 1 to 3, characterized   in that the radial arm (7) of the shield (5) is provided with a guide pin (17) penetrating into the radial groove (3) of the   oscillating wheel (1) and acts on the bearing (15) of the oscillating wheel.   6. Clutch device according to claims 1 to 3, characterized   in that the framer (5) is wedge-shaped and comprises two radial branches (7, 7 '), a radial branch (7) acting on the plane faces of the radial groove (3) of the oscillating wheel (1) or on the rear plane face of said wheel (1) and the second limb   radial (7 ') on the rear planar face of the fixed wheel (2).   7. Clutch device according to claims 1 to 3, characterized in that the radial branches (7, 7 ') of the framer (5) are 26020 19   symmetrical or asymmetrical with respect to the meshing point of the wheels (1, 2) of the gear.   8. Clutch device according to claims 1, 2, 3 and 7, characterized in that the section profiles of the groove (3) of the wheel   oscillating (1) and the radial branch (7) are rectangular, triangular or circular, concave or convex profiles. 9. Clutch device according to claim 2, characterized in that   that the axial branch (6) of the framer (5) is straight or bent.   10. Clutch device according to claims 2 and 9, characterized in that the right axial leg (6) of the framer (5) penetrates   in an indentation of the plane face of the primary drive (10) and the bent axial branch (6) of the framer (5) in a   notch of the envelope surface of the primary drive (10).   11. Clutch device according to claim 1, characterized in that the radial branches (7) of the framer (5) have a recess (22) into which the cleat (9) of the element command (8).   12. Clutch device according to claim 1, characterized in that   the control element (8) has two cleats (9, 9 ') which act on the outer end faces of the framer (5).   13. Clutch device according to claims 1 and 12, characterized in that the lugs (9, 9 ') are integral with the primary drive (10).   14. Clutch device according to claims 1 and 2, characterized in that the catches (9, 9 ') are integral with the control element (8).   15. Clutch device according to claims 1 and 12, characterized in that the cleats (9, 9 ') are mounted in rotation or   axial translation on the control element (8) and prestressed. 30 16. Clutch device according to claims 1, 12, 14 and 15,   characterized in that the catches (9, 9 ') penetrate into indentations (21) of the primary drive (10).   17. Clutch device according to claims 1, 2, 4 and 5,   characterized in that a thrust washer (16) is disposed between the radial branches (7) of the framer (5) and the bearing (14).   the primary drive or the bearing (15) of the oscillating wheel.   18. Clutch device according to claims 1 to 7, characterized   in that the radial branches (7; 7 ') of the framer (5) have central notches.