FR2558514A1 - DRIVE DEVICE FOR POWER TRANSMISSION CABLE OR WIRE MECHANISM - Google Patents

Abstract

THE DEVICE ACCORDING TO THE INVENTION, ALLOWING THE AUTOMATIC REGULATION OF THE TENSION OF THE WIRES 32, 33, INCLUDES A DRUM 4 MOUNTED IN ROTATION IN A BOX 1, 2. ON A FIRST SIDE SURFACE, THE DRUM HAS A FIRST LOCKING TEETH 7 AND, ON A SECOND SIDE SURFACE, IT SHOWS A FIRST PART OF ENGAGEMENT 10 RETAINING AN END 9 OF A WIRE 32. ITS PERIPHERAL SURFACE CONSTITUTES THE WINDING SURFACE OF THE WIRES 32, 33. A RATCHET PLATE 5 IS ADJACENT TO THE DRUM 4 AND HAS A SECOND SNAP TOOTHING 12 ENGAGED WITH THE FIRST 7, AS WELL AS A SECOND ENGAGEMENT PART 14 RETAINING THE END 13 OF THE SECOND WIRE 33. A SPIRAL SPIRAL 19, MOUNTED BETWEEN THE RATCHET PLATE 5 AND THE BOX, RECALLS PLATE 5 IN A DIRECTION OF ROTATION ALLOWING FREE MOVEMENT OF THE TEETH 7, 12. AN ELASTIC BODY 25 RECALLS DRUM 4 TOWARDS RATCHET 5. A SHAFT 3 ROTATES THE DRUM 4. APPLICATION A THE EQUIPMENT OF F REGULATORS ENETRE, ESPECIALLY FOR AUTOMOBILES.

Description

The present invention relates to a training device used in

  a mechanism for regulating the closing or opening operation of a window, hereinafter called window regulator memory, and the invention relates more particularly to the device

  which can automatically eliminate the release

  ment, the slackening or the permanent elongation of cables, and which can always maintain the tension of the cables in one

suitable range of values.

  11 c Until now, a window regulator has been used, in which flexible cables are used as means of power transmission, in the doors of motor cars or the like. For example, a window regulator is known as shown in FIG. 24. More specifically, the window regulator comprises two cables 81, 82 which are laid in the window regulator in the stretched state, a driving device 84 having a drum 83 for winding cables 81 and 82 in opposite directions, and to which one end of each cable is connected, and a driven device 87 having a carrier plate 86 capable of sliding on a guide rail 85, and to which the other end of each cable 81, 82 is connected. When the drum 83 is rotated in the direction of the arrow A or B, one of the cables 81 and 82 is wound around the drum 83 and the other cable is unwound from the drum 83, and, consequently, the plate carrier 86 moves in the direction of arrow C or D. However, elastic elongation and permanent elongation generally occur in cables, such as

  as metallic stranded cables, during operation

  is lying. If permanent elongation and / or slackening or relaxation occurs in the cables, the tension in the cables is lost and it is impossible for the drive device 84 to correctly transmit the force of 3S. Operate to the driven device 87 Such a loosening or such permanent lengthening of the cables leads to the following drawbacks: for example, a window pane is shaken from top to bottom due to the vibrations of a car, or of a similar vehicle;

  an operating crank is shaken due to vibrations

  In a car or similar vehicle, the window glass is stained because the greased cables come into contact with the window glass, and a noise of

  whipping from cables is produced in the gates

  due to vibrations from the car or motor vehicle. Such inconvenience bothers the driver or

  its passengers. In addition, loose or loose cables tend to

  tooth to be released from a guide member or a pulley intended to guide the cables, and the latter tend to be damaged. As a result, the window regulator becomes

occasionally inoperative.

  For these reasons, various means have already been proposed previously for eliminating the loosening, relaxation or permanent elongation of the cables, in order to regulate

suitable cable tension.

  For example, a regulatory mechanism has already been proposed

  tensioning lation, intended to increase the length of the cable trajectory, by means of a spring urging an external casing (conduit), capable of sliding a cable, towards an associated member with which the external casing is intended to be associated, at one end of the external casing, or by means of a tension pulley. In addition, Italian Patent No. 927,030 (corresponding to British Patent No. 1,382,330) describes another mechanism which can eliminate

  loosening or relaxing the cables by means of a rotation

  manual operation of a ratchet plate in relation to the drum.

  The ratchet plate is adjacent to a cable winding drum with snap-in teeth and engaged with

one end of a cable.

  However, with regard to the first mechanism presented above, there is a problem in that it is somewhat difficult to operate the device, since the cable is always tight. Regarding the last mechanism presented above, it

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  arises a number of problems because it is practically

  unable to regulate cable tension after the

  nism be installed inside a car door

  automobile or similar vehicle.

  In order to eliminate the above drawbacks, mechanisms for automatically eliminating permanent stretching which has occurred in cables are disclosed in U.S. Patents 4,400,993 and

4,440,354.

  The mechanisms comprise, as basic elements, two divided drums, that is to say a first drum and a second drum having snap teeth 93, 94 on each side face, as indicated by the line in broken lines on Figure 24. The mechanisms can eliminate permanent elongation by means of a relative rotation of the first drum 83a and the second drum 83b. However, the mechanism does not fulfill any balancing function between the

  window glass lifting force and lowering force

  window glass, nor does it fulfill the function of reducing the lifting force of the window glass, since a spiral spring is not used. Regarding the mechanism, even if there is a spiral spring, the size of the spiral spring is limited by the size (diameter and depth) of the cavity formed in the second pulley. As a result, the spiral spring is not

  significantly used in the last mechanism presented below

  above, except in the form of a spiral spring, the diameter of which

  meter and width are small, that is to say that the restoring force of the spiral spring is low. More specifically, the relative rotation of the first pulley and the second pulley is caused by a torque supplied by a crank, by a braking force, that is to say a friction resistance which is applied to the second pulley when the first pulley is driven in rotation, and by the return force of the spiral spring. However, the friction resistance is not a suitable element, since the friction resistance depends on different conditions, for example the roughness of

25 585 14 4

  each contact surface, the pressure between the pulleys,

  the existence of a certain grip on the sliding portions

  health, and similar parameters. Likewise, the friction resistance changes due to the abrasion produced during operation. As a result, there is occasionally a very wide dispersion of the voltage values. In addition, the work consumed by the operation is important in the case where the second pulley is rotated, because the friction resistance is applied to the second pulley

  not only in one direction but also in the opposite direction.

  In order to solve the problems presented above, it is desirable to use a spiral spring having as high a return force as possible. More precisely, if the restoring force of such a spiral spring rotates the latching toothing in a direction of "free movement", the tension can be regulated more precisely, and the work required for operation can be reduced, by comparison with the above mentioned case involving the intervention of the

friction resistance.

  The terms "free movement" or "free movement" used in the remainder of this specification mean that, when a torque is developed due to the relative rotation of a first detent teeth and a second detent teeth thanks to upon rotation of a crank, sloping portions of the first latching toothing and the second latching toothing slide in the direction of rotation over one another, and the two latching toothing move axially in opposite directions with respect to each other, and finally the snap teeth again engage with each other. In addition, the terms "free movement" or "free movement" correspond not only to a case in which a latching toothing moves in an axial direction and rotates around the axis, but correspond to different cases, for example to a case in which one latching toothing moves in an axial direction while the other latching toothing rotates about the axis, or in a case in which the two latching toothing moves axially in a direction which take them away

  on the other, and in which one of the two click teeth -

  or both rotate around the axis in opposite directions.

  On the other hand, when the spiral spring is adapted to support the weight of the window pane or to balance the lifting force of the window pane with the lowering force of the window pane, the force Reminder intended for balancing is not sufficient, because the size of the spiral spring is limited by the size of the cavity formed in the second conventional pulley. In this regard, it is desirable that the restoring force of the spiral spring be increased as much as possible. In particular, it is desirable that the diameter, in the mounting configuration, of the spiral spring be as large as possible in order to

  limit the total thickness of the mechanism.

  However, it is desirable to reduce the operating force of the crank by increasing the ratio of the length of the crank to the diameter of the second pulley, for example by reducing the diameter of the pulley. In order to simultaneously satisfy these contradictory requirements, it is conceivable to take the spiral spring out of the cavity formed in the second pulley, and to arrange it in another part. However, in this case there is a problem

  insofar as the total thickness of the driving device

ment is increased.

  In addition, in the case where the device is used

  tif of drive mechanisms as presented above

  and fitted with snap teeth, it occurs occasionally-

  excessively elastic elongation. For example, when the sliding resistance between the carrier plate 86 and the guide rail 85 temporarily increases, or when the crank 91 is turned in the direction of arrow B after

  that the first target 81 has been fully wound up (i.e.

  say after the carrier plate 86 has reached the stop 88), the relative rotation of the first drum 83a and the second drum 83b3 is carried out excessively. This results in the development of excessive elastic elongation in the first cable 81 (and in the second cable 82). In addition, consequently, the grip of the snap teeth 93 and 94 can advance in a configuration which eliminates any play.

  suitable. It is disadvantageous that such an elongation-

  excessive ticking of the cables leads to permanent elongation,

  and causes the pulley 89 and the rotational shafts to flex

  tion of other connecting members, and this has the consequence

  that the operation of the crank 91 is difficult.

  Similarly, in the case where the crank 91 is turned in the direction of the arrow A, if the sliding resistance mentioned above increases or if the crank is turned in the direction of the arrow A after the carrier plate 86 has reaches the opposite stop 90, the snap teeth 93 and 94 rotate freely on one another, despite the grip or snap direction of the two snap teeth (this phenomenon is designated hereinafter by the terms "freewheeling phenomenon"). The freewheeling phenomenon causes the cables to loosen. Freewheeling phenomenon tends to occur due to wear of the teeth heads

93 and 94.

  Furthermore, a mechanism is known for eliminating permanent elongation or slackening of the cable, and which comprises a braking spring (for example a spring

  brake 114 in FIG. 25) arranged between the drive shaft

drag 95 and drum 83.

  The brake spring 114 shown in the figure is used to prevent the raising or lowering of a window pane (for example a window pane 100 in Figure 24), except when the crank 113 or the tree

  112 is positively driven in rotation. In such a provision

  tif of drive, implementations of the brake spring

  114 are, as described below, insured by means of the asso-

  ciation of a notched part 118 of an association member 117 and an association projection 19 of the drum 108 with a certain

  clearance, for example an angle of 30, in the direction of rotation.

  In this case, the drum 108 is not fixed to the shaft 112, and

  the associated member 117 is fixed to the shaft 112.

  As shown in Figure 25, when the handling

  velle 113 is turned in the direction of arrow A, a lateral surface 118a of the notched part 118 pushes a point 114a of the brake spring 114 in the direction of arrow A. Consequently, the locking operation of the brake spring (due to the friction resistance of the brake spring and an internal peripheral surface of the boot) is released, because the diameter of the brake spring 114 is reduced. Consequently, since the rotation of the association member 117 causes the notched part 118 and the association projection lg19 to cooperate with each other, the drum 108 can be rotated in the direction of the arrow A. A rotation of the crank 113 in the direction of arrow B also results in the release of the action of

  locking ensured by the brake spring.

  Even if you try to raise or lower the window

  window 100 (see figure 24) without turning the handle

  velle 113, the brake spring 114 fulfills the locking function, because the diameter of the brake spring 114 increases, and the association projection 119 of the drum 108 pushes

  the tip 114a or 114b of the braking spring 114.

  As described above, with regard to the operation

  Locking or unlocking ration, it is necessary that one point moves to a certain extent before the other point moves, in order to increase or decrease the diameter of the brake spring. To this end,

  it is necessary to have some clearance between the projection of as-

  sociation 119 and the indented part 118, in the direction of rotation. If there is no play between these elements, the two

  points 114a and 114b are rotated at the same time, and therefore

  that the diameter of the brake spring 114 cannot be

  neither increased nor decreased. As a result, the locking operation

  the operation and the unlocking operation are not ensured.

  Consequently, the shaft 112 is rotatable on the allowed play range, against the shoemaker 111, without rotating the drum 108 itself. In this case, the crank 113 fixed to the end of the shaft 112 is also likely to be

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  moved at an angle of about 30.

  Thus, when the window regulator is installed in a motor vehicle or similar vehicle, there is a problem that the crank 113 can oscillate or make noise due to vibrations from the car or vehicle. This causes some annoyance which is felt

by the driver.

  In addition, the tremors undergone by the crank 113 cause the tips 114a, 114b of the braking spring 114 to receive repetitive pulsating forces. Another problem is posed by the fact that the repeated pulsating forces cause some fatigue damage of the tips 114a and 114b. Therefore, the operation of the regulator

  window cannot be guaranteed.

  As a method of solving the problems mentioned above, it is possible to envisage increasing a resistance of

  friction between the shaft 112 and the boot 111, or the resistance

  friction between the shaft 112 and the drum 108, but it is difficult to maintain the friction resistance within a suitable range, and it is not useful to increase the

  frictional resistance because this makes the operating force

  vre too important, and, moreover, it causes the wear of the

slippery parts.

  The main object of the present invention is to

  propose a training device usable in a regu-

  window reader and which can prevent a window

  crank to be subjected to tremor and shaking.

  Another object of the present invention is to provide

  be a drive device usable in a window regulator that can always keep cables under tension

within a suitable range.

  Another object of the invention is to provide a mechanism which can satisfy conflicting requirements, namely the use of a spiral spring having a large diameter, increasing the ratio of the length of the crank to the diameter of the pulley (hereinafter referred to as the "lever ratio"), and the reduction of the thickness of the mechanism, and in which the function of regulating the tension of the cables and the function of balancing the lifting force of the window glass and the lowering force of the window glass are provided on a regular basis.

  According to the invention, the drive device

  ment, usable in a window regulator, 9 comprises (a) a shoemaker; (b) a drum mounted in rotary movement in the case, and having a first lateral surface having a first latching toothing, a second lateral surface having a first engagement part intended to retain a first cable end, and

  a peripheral surface acting as a winding surface

  also cables; (c) a ratchet plate adjacent to and coaxial with the drum, this plate having a surface provided with a second latching toothing in engagement with the first latching toothing of the drum, and a second engagement part intended retaining a second cable end; (d) a spiral spring having one end engaged in the ratchet plate and having its other end engaged in the case, and recalling the ratchet in such a direction that the first latching toothing and the second latching toothing are freely moved; (e) an elastic member axially recalling the drum towards the ratchet plate; and (f) a shaft intended to rotate the drum by

engagement with the latter.

  Furthermore, in accordance with the present invention, it is

  offers a training device that can be used in a regu-

  window reader and comprising: (a) a housing; (b) a drive member comprising a shaft mounted in rotation in the casing and an association member fixed to the shaft, 2org of extension extending from the shaft, in radial direction, and having at less a notched part along a peripheral edge of the associated member; (c) a drum being mounted in the case and being adjacent to the association member, this drum being coaxial with the shaft, rotatably mounted around the shaft, and having a mounting projection which is drilled on a first surface lateral of the drum facing the associaticn member and being able to cooperate with the indented part, with a certain play in the direction of rotation; and (d) an elastic member recalling the association member in the direction of rotation, by the engagement of one end of the elastic member against the drum and by the engagement of the other end of the member. elastic against the drive member. 15. In addition, in accordance with the present invention,

  offers a training device that can be used in a regulation

  window guard and comprising: (a) a housing; (b) a drive member comprising a shaft rotatably mounted in the housing and. an association member qUi is fixed to the tree, the association member extending from the tree in the radial direction and having at least one notched part along a peripheral edge of the association member

  (c) a drum being mounted in the housing, in position

  tion adjacent to the association member and coaxial with the shaft, this drum being rotatable around the shaft, movable axially along the shaft, and having an association projection,

  which is hay on a first lateral surface of the drum

  bour who faces the association organ, and is capable of co-

  pererating with the indented part, with a certain play in the direction of rotation, the drum having a first snap-toothing on a second lateral surface which is opposite to said first lateral surface of the drum; (d) a latching member being mounted in the housing, in position adjacent to the drum, being coaxial with the shaft, and mounted to rotate around the shaft, this latching member having a second latching toothing on a first side surface which faces the drum, the second latching toothing being intended to engage the first latching toothing; (E) a spiral spring being located between the latching member and the case so as to return the latching member in the direction of free movement of the first latching toothing and the second toothing snap; (f) an elastic member disposed between the drum and the de.manière association member. to recall the association body in the direction of rotation; (g) a first cable having one end engaged in the drum and a second cable having one end engaged in the latching member; and (h) a first thrust projection and a second thrust projection being mounted on the two lower sides of the association projection and being capable of being introduced between the bottom surfaces of the association member and the first surface side of the drum, respectively. In this way, we can eliminate loosening and permanent elongation,

  the cable tension being kept within a suitable range

  ble due to the fact that the freewheeling phenomenon is prevented, and tremor and jolts are surely avoided

a crank.

  The objects and advantages of the present invention, as well as other objects and advantages, will result from the

  description which follows, given without limitation in reference

Refer to the accompanying drawings.

  In these drawings: - Figure 1 is a perspective view with a partial cutaway, representing an embodiment of the drive device of the invention, - Figure 2 is an exploded perspective view of the embodiment of the device d drive of the invention which is shown in Figure 1, - Figure 3 is a front view showing a window regulator comprising the drive device

12 5

  according to the invention, - Figure 4 is a perspective view showing another embodiment of a drum of the drive device according to the invention, - Figure 5 is a perspective view showing

  another embodiment of a ratchet plate of the provision

  training device of the invention, - Figure 6 is a side elevational view

  partially cut off from another embodiment of the provision

  training device according to the invention, - Figure 7 is a perspective view showing

  yet another embodiment of the driving device

  ment according to the invention, - Figure 8 is an exploded perspective view of the embodiment of the drive device according to the invention which is shown in Figure 7, - Figures 9 to 14b are diagrams showing the steps of the operation of the drive device according to the invention shown in Figure 7, - Figure 15 is an exploded perspective view of another embodiment of the drive device according to the invention, - Figure 16 is a c8té view partly in section of another embodiment of the drive device according to the invention, - Figures 17 and 18 are front views of a window regulator comprising the drive device according to l invention, - Figure 19 is a perspective view partly in section showing yet another embodiment of the drive device according to the invention, - Figure 20 is a partial front view of the drive device according to l represented invention in Figure 19, - Figure 21 is a side view partly in section of the drive device according to the invention shown in Figure 19, - Figures 22 and 23 are respectively a partial front view and a side view in sectional view showing operating steps of the drive device of the invention shown in FIG. 19, - FIG. 24 is a perspective view showing a window regulator of the state of the art, and - FIG. 25 is an exploded perspective view

  a training device of the state of the art.

  In Figures 1 and 2, references 1 and 2 desi-

  Io gnent respectively a first and a second boot, An overall boot consists of the first boot 1 and the second boot 2. The boot contains and rotatably supports a rotary shaft 3. A drum 4 and a ratchet plate 5 are mounted rotating on the shaft 3 and are adjacent one

  to the other. The drum 4 is capable of moving in the direction

axial position on the shaft 3.

  A first lateral surface 6 of the drum 4 is provided with a first latching toothing 7. A second lateral surface 8, which is a surface opposite to the first

  lateral surface 6, is provided with a first engagement part-

  ment in which a first cable end 9 is engaged. A first lateral surface 11, adjacent to the drum 4, of the ratchet plate 5 is provided with a second latching toothing 12, capable of engaging with the first latching toothing 7, and a second part d engagement 14, in which a second cable end

13 is engaged, respectively.

  A boss 16, which has a first engagement groove 17, projects on a second lateral surface 15 of the ratchet plate 5. In addition, an external peripheral surface of the second shoemaker 2 has a second groove

of engagement 18.

  A spiral spring 19 is housed in the second case 2. The two ends 20 and 21 of the spiral spring 19 are intr,. Duiltes respectively in the first engagement groove J7 and in the second engagement groove 18. The spiral spring 19 recalls the ratchet plate 5 in such a direction that a free movement is obtained, that is to say a movement in the direction of the arrow A. A member of association22, of cupular shape, is fixed to the shaft 3, and a fan-shaped scalloped part 23 is formed on the cylindrical lateral part of the association member 22. The second lateral surface 8 has a projection

  24 capable of cooperating with the notched part 23 in the event

  tail, with a certain play in the direction of rotation.

  An elastic member, for example a coil spring 25, is housed between the drum 4 and the member 22 ensuring the association. The helical spring 25 recalls axially

  the drum 4 towards the ratchet plate 5.

  One end 26 of the shaft 3 protrudes beyond an orifice 27 of the first housing 1, and a crank 28

  is attached to the end 26 of the shaft 3. A brake spring

  swim 29, which is known in a conventional manner, is mounted between an internal peripheral surface of the first housing 1 and an external peripheral surface of the member 22 ensuring the association, and the two ends 30 and 31 of the braking spring 29 are introduced in intervals between the scalloped portion 23 in a fan shape and the projection 24 ensuring

association, respectively.

  A peripheral surface of the drum 4 is used as the cable winding surface 36 in order to wind a first cable 32 and a second cable 33. The first cable 32 and the second cable 33 are spirally wound in the same direction (in the case of Figure 2, in the same direction as a screw whose propeller is turned to the left). The first cable end 9 of the first cable 32 is engaged in the first engagement part 10. The first cable 32 is helically wound towards the first lateral surface 6, moves away from the drum 4 on its path, and is guided in a first outer casing 35, passing through a first guide groove 34 of the second case 2. The second cable end 13 of the second cable 33 is engaged in the second engagement part 14 of the plate & ratchet 5. The second cable 33 is wrapped around the winding surface 36 from the side of the first lateral surface 6 and towards the side of the second lateral surface 8, then it moves away from the drum 4 on its path, and is guided in a second envelope

  external 38 passing through a second guide groove 37.

  The other end of the first cable 32 and the second cable 33 is engaged in a carrier plate 41 of a driven part

  window regulator 39, as described below.

  Consequently, the first cable 32 and the second cable 33

  substantially form a closed loop.

  The functions of the device will be described below.

  drive according to the invention. In order to clearly describe

  the functions of the drive device, the device

  drive used in window regulator 39 shown

  shown in Figure 3 is described as a typical case.

  However, the use of the training device according to

  the invention is not limited to this typical case. More precise-

  The mechanism can be applied in different arrangements.

  sitives using cables as power transmission means, In FIG. 3, the reference 42 designates a drive part of the window regulator 39. The drive part 42 is connected to the driven part 40 by means of two cables control 43 and 44. The drive device according to the present invention is contained in the drive part 42. The driven part 40 comprises

  a guide rail 45 and a carrier plate 41 slidably mounted

  health on the guide rail 45. In order to change the direction of movement of the cables 32 and 33, a cable guide (or a pulley) 46 is mounted on the upper end of the guide rail

  45. Similarly, in order to change the direction of movement-

  cable 32, a pulley (or cable guide) 47 is mounted

  on the lower end of the guide rail 45.

  The control cable 43 comprises a first wire or wire 32, hereinafter called wire, and a first outer casing 35 for guiding the first wire 32 in sliding, and, similarly, the control cable 44 comprises a second cable or wire 33, also

  hereinafter called wire, and a second external envelope 38.

  That is, the control cables 43 and 44 are

traction control cables.

  As regards the window regulator 39, produced as described above, when the crank 28 is turned in the direction of the arrow A, the second wire 33 is wound around the drum 4 and the first wire 32 is unwound from this drum 4 Consequently, the closed loop circulates in the direction of arrow C, and a window pane G fixed

  to the carrier plate 41 is raised. In the event that the

  velle 28 is turned in the direction of arrow A, the drum 4 and the ratchet plate 5 rotate together in the same direction, because the first detent toothing 7 and the second toothing

  latching 12 are firmly engaged with each other.

  In addition, when the crank 28 is turned in the direction of the arrow B, the first wire 32 is wound around the drum 4 and the second wire 33 is unwound from this drum 4. Consequently, the closed loop circulates in the direction of arrow D, and window glass G is lowered. In this case, although the direction of arrow B is the direction of free movement, the drum 4 and the ratchet wheel 5 rotate together in the same direction, because the second wire 33 pulls the ratchet plate 5 in rotation, and the fact that the helical spring recalls the drum towards the ratchet wheel and causes the ratchet wheel to be rotated in the direction of arrow B. Like the length of the part of a wire wound around the drum 4 is equal to the length of the part of the other wire which is unwound from the drum 4, regardless of the direction of rotation, the first wire is wound on the part

  from which the other thread was previously unwound. This is-

  that is, the drive device according to the invention has only one winding surface 36 instead of two winding surfaces for winding two wires. For this reason, the thickness of the drum 4 can be limited to a small value. As a result, as detailed below, even

  if a spiral spring 19 having a large diameter in configuration

  mounting and the drum 4 are arranged axially in a row, the total thickness of the mechanism can be limited to

a low value.

  The function of automatic elimination of the loosening of the wires 32 and 33 will be described below. In the case where the loosening occurs in the wires, when the drum 4 is turned in the direction of the arrow B by a rotation of the crank 28 in the direction of arrow B, the second wire 33 does not pull the ratchet plate 5 in the direction of arrow B. In addition, the ratchet plate 5 is in a state suitable for being braked by the restoring force spiral spring 19 in the direction of arrow A

  and, moreover, due for example to the friction resistance

  ment between the ratchet plate 5 and the shaft 3. For this reason, the drum 4, which receives a torque in the direction of the arrow B, moves towards the second lateral surface 8, in the axial direction, against of the return force of the coil spring dal 25. The first snap teeth

  7 climbs on the second click teeth 12, and final-

  ment the first latching toothing 7 and the second latching toothing 12 again engage with each other in the new position, offset by the value of a tooth relative to the previous position, due to of the return force of the helical spring 25. As a result, free movement occurs. Consequently, only the drum 4 rotates in the direction of the arrow B, so that the rotation

  relative of the drum 4 and the ratchet wheel 5 is ensured.

  For this reason, the second wire 33 slides on the winding surface 36 of the drum 4, and is pulled outwards towards the side of the second engagement part 14. It

  results in loosening of the wires.

  After the tension in the threads has been restored, the ratchet plate 5 and the drum 4 are again driven

together in rotation.

  vif3 Regarding the drive device de.invention in the case where the return force of the Soiraki spring 19 is higher than the force necessary to ensure that the first snap teeth 7 and the second teeth snap 12 move freely (the force required also depends on the return force of the coil spring 19 and the angle of inclination of each tooth-snap teeth 7 and 12), as described below, the spring hairspring 19 drives the ratchet plate in positive rotation in the direction of arrow A, and this hairspring spring 19 also gives the braking force to the ratchet plate 5. For these reasons, the tension of the threads is more precisely regulated . In this case, the crank

  28 can be immobilized in position.

  In other words, when there is a relaxation

  Chely in the wires, the ratchet plate 5, which is recalled by the spiral spring 19 in the direction of arrow A, is rotated in the direction of arrow A due to the free movement. As a result, the second end 13 of wire is pulled in the direction of arrow A, the second wire 33 is pulled and released from the winding surface 36 of the drum 4, and, finally, the first latching toothing 7 and the second latching teeth 12 engage with each other by means of the helical spring 25, in a position such that the tension of the wires is proportional to the restoring force of the helical spring 25. Consequently,

  as the loosening of the threads is eliminated, the tension

  thread count is restored. When only the ratchet plate is rotated by the spiral spring 19, the drum 4 is braked by the restoring force of the braking spring 29, or by the friction force between the drum

4 and tree 3 ..

  In the case where the crank 28 is immobilized, the operation of eliminating the slackening of the cables tends to be obtained in a state such that the drum 4 is sufficiently rotated in the direction of the arrow B. This is based on the following reasons: the restoring force of the spiral spring 19 is increased in proportion to the winding amplitude of this spiral spring, and moreover,

  the amplitude of the winding of the second wire 33 around the drum

  bour 4 is weak in the state described above.

  In the case where the drive part 42, comprises

  as the drive device according to the invention is connected to the driven part 40, so that the direction in which the spiral spring 19 recalls the ratchet plate 5 corresponds to the direction in which the window pane G is raised, the spiral spring 19 works like a spring

known balancing.

  In other words, since the spiral spring 19 always recalls the closed loop of the wires in the direction of the arrow C shown in FIG. 3, the weight of the window pane G is balanced by the restoring force of the spiral spring 19 For this reason, the operating force of the crank 28 has nothing to do with the directions of rotation of the crank 28, and the operation is made easier. In addition, the work required to raise the window glass G is reduced. In this case, when the window pane is lowered, the spiral spring 19 is banded. On the other hand, when the window glass is raised, the spiral spring

19 is relaxed.

  In the drive device of the invention, the spiral spring 19 is arranged in series with the drum 4 and the ratchet plate 5, without being housed in the drum 4. For this reason, the lever ratio can be increased by reducing the diameter of the drum 4. In addition, the balancing function is well fulfilled by adopting a spiral spring

  which has a large diameter in mounting configuration.

  Also also, the thickness of the drum 4 can be limited to a small value, that is to say that the total thickness of the drive device can be limited, because the drum 4 serves as a double winding drum for the first thread

32 and for the second wire 33.

  As the diameter of the spiral spring 19 is not limited by the diameter of the drum 4, the diameter of the spiral spring 19, in the mounting configuration, can be chosen larger than the diameter of the drum 4. For this reason, it is possible to use a spiral spring having a high return force. In this case, as shown in FIGS. 1 and 2, if the shoemaker consists of two divided shoemakers, that is to say of the first shoemaker 1 intended to contain the drum 4 and of the second shoemaker 2 intended to contain the spring

  hairspring 19, it is easy to assemble the drive device

  is lying. The ratchet plate 5 can be housed in the second case 2. In addition, as shown in FIG. 6, the

  ratchet plate 5 can be accommodated in the first case 1.

  In the drive device shown in FIGS. 1 and 2, the second engagement part 14 is situated outside the second latching toothing 12, but it is desirable to make the second part of engagement 14 is close to the center of rotation, in order to effectively use the restoring force of the

spiral spring 19.

  Referring to FIGS. 4 to 6, the following will be described:

  below preferred embodiments of the device

according to the invention.

  In the drum 51 shown in Figure 4, a portion 52 of the winding surface which is adjacent to the first side surface extends to the interior of the first latching toothing 7. In this case, even if the first latching toothing 7 is partially destroyed, for example if the first latching toothing is not a latching toothing in the form of a complete ring, the function of the first latching toothing

can be preserved.

  In FIG. 5, the ratchet plate 53 which is associated

  ciée to the drum 51 in Figure 4, is shown. In

  in this case, the second engagement part 54 is located inside

* laughing at the second click teeth 12.

  In addition, as shown in FIG. 5, when a guide surface 55 is formed as a part extending the second engagement part 54, the guide surface 55

  can advantageously guide part of the wire which is already

center at the end of the wire.

  In the mechanism shown in Figure 6, a

  drum 56 has a cylindrical groove 57 which is concentric

  than. In addition, the drum 56 includes a guide channel (not shown in the drawing) which is similar to the part 52 (shown in Figure 4). The ratchet plate 58 presents

  a cylindrical projection 59 which is engaged in the cylindrical groove

  drique 57. The cylindrical projection 59 has a second engagement part 60. An external peripheral surface 61

  of the cylindrical projection 59 is arranged on the winding surface

lie sons.

  Due to the structure of the mechanism described above,

  part of the wire can be wound on the peripheral surface

  that external 61 of the cylindrical projection 59, conti-

  naked, due to the movement in which the drum 56 and the ratchet plate 58 rotate in opposite directions with respect to each other. Consequently, even in the case of a significant increase in the amplitudes of relaxation or elongation

  permanent wires, the mechanism can be sufficiently reliable.

  In the embodiments described above, it is desirable for the winding surface of the drum to have a helical winding groove (for example the part marked with the reference 62 in FIG. 4), so that the wires are rolled up so as not to be tangled

with each other.

  As regards the drive device according to the invention, when the second engagement part 14 is higher than the second latching teeth 12, in the axial direction, the second wire 33 does not interfere with the teeth d snap-fitting 7 and 12. Such a preferred embodiment can be produced, for example, by projecting the second engagement part 14 from the surface of the ratchet plate 5, as shown in FIG. 2 or in the figure, or by forming the second engagement part 60 inside the cylindrical projection 59, as shown in FIG. 6. In this case, the part of the winding groove 62 which is closest to the first lateral part 6 is produced in the form of a circular groove instead of a

helical groove.

  As described above, in accordance with the invention,

  a spiral spring with a larger diameter can be used

  meter and, consequently, having a greater restoring force; the leverage ratio can be increased; the thickness of the drive device can be limited, and, consequently, the function consisting in regulating the tension of the threads as well as the function consisting in balancing the force necessary for lifting a window pane by the force necessary for the window glass lowering

  can be provided smoothly and on a regular basis.

  Figures 7 and 8 show an embodiment

  tion of the drive device according to the invention which is similar to the drive device shown in Figures 1 and 2. For this reason, with regard to the same parts as those q.ui are shown in Figures 1 and 2 , the same reference numbers are used and

  their detailed description is omitted.

  In FIGS. 7 and 8, a member of association of

  cup shape 22 is fixed to the shaft 3, and an exchanging part

  creates in fan 23 is formed in the side cylinder

  the association organ 22. A training organ

  consists of the shaft 3 and the association member 22.

  The second lateral surface 8 of the drum 4 has an association projection 24 capable of cooperating with the indented part 23 of the association member 22, with a certain

play in the direction of rotation.

  A coil spring 25 is disposed between the drum

  4 and the association member 22, as an elastic member.

  The helical spring has folded end portions 25a, 25b. One end part 25a is engaged in the association member 22 and the other end part

b is engaged in the drum 4.

  The helical spring 25 recalls the drum 4 which is axially movable along the shaft 3, towards the side o is the ratchet plate 5, and it also recalls the drum 4 in the direction of the arrow B, c ' is to say in

  the direction of rotation of the free movement.

  The two bottom sides of the association projection have a first thrust projection 65 and a

  second thrust projection 66 (shown in Figure 8).

  The first thrust projection 65 is situated on the lateral part where the rotation of the association member 22 in the direction of the grip of the latching teeth 7 and 12 causes the notched part 23 to push the association projection 24. An upper part (marked at 65a in FIG. 14a) of the first thrust projection 65 is preferably inclined, so that it is easy for the first thrust projection 65 to slide in a delimited interval between the surface of the below 22a (see FIG. 12) of the association member 22 and the second lateral surface 8 of the drum 4, that is to say that it is easy for the drum 4 to move axially towards the ratchet plate 5 In this way, the last operation described above, consisting

  to eliminate sagging wires, is made easier.

  When the indented part 23 cooperates with the association projection 24, due to the rotation of the crank 28, an axial force is exerted in the direction of the arrow Q, so that a pushing force of the drum 4 towards the ratchet plate 5 is increased, and, for this reason, the grip of the snap teeth 7 and 12 is more assured. As a result, we more effectively avoid

the freewheeling phenomenon.

  In addition, the second thrust projection 66 preferably has a small inclined part or a small rounded part 66a (see FIG. 14), so that the introduction

  of the second thrust projection 66 in a defined interval

  mapped between the bottom surface 22a and the second surface

  lateral 8, or the exit of this projection 66 from this inter-

  valle are provided regularly and smoothly.

  The shapes and numbers of the first push projection 65 and the second push projection 66 are not limited. For example, as shown in FIG. 15, two first thrust projections and two second thrust projections may be arranged respectively on a circular line. In this case, the association member 22 may have a notched part 23a which is located on the side opposite to the notched part 23, and which is arranged in a part corresponding to the thrust projections 65 and 66. In general, it it suffices to provide a first thrust projection 65 and a second thrust projection 66 on the circular line. Similarly, a relatively small number of association projections can be mounted on the drum, and, in this case, the association member has scalloped parts

  number corresponding to that of the association projections.

  As shown in Figure 8, one end 67 of the shaft 3 is inserted into an opening 27 of the first

  boftier 1, and a crank 28 is fixed at the end 67.

  In addition, a conventional brake spring 29 is mounted.

  between an external peripheral surface of the associative organ

  tion 22 and an internal peripheral surface of the first boot 1, and the two ends 30 and 31 of the braking spring 29 are introduced in the intervals which exist between the

  indented part 23 and the association projection 24, respectively

  vement. As shown in FIG. 9 and in the figure, in the case where no torque is exerted on the crank 28, the lateral surface of the notched part 23 is in contact with the lateral surface of the projection association 24. The first recalls the second. In addition, it is not easy to rotate the drum 4 itself, because of the reception of the tension of the wires 32 and 33. For this reason,

  the crank 28 is not subjected to shaking.

  While the crank 28 is rotated in the direction of arrow A or in the direction of arrow B, the first thrust projection 65 or the second thrust projection 66 is in the state of being engaged between the bottom surface 22a or 22b of the association member 22 and the second lateral surface 8 of the drum 4 (as shown in FIG. 14a and in FIG. 14b). As a result, the drum 4 cannot move towards the side of the association member 22, on the shaft 3, and the drum 4 is pushed towards the ratchet plate 5. In this way, the freewheeling phenomenon of the snap teeth 7 and 12, and there is no excessive elastic elongation of the wires 32

  and 33 which would be due to free movement.

  In the training device of the invention, the slackening of each wire 32 and 33 is eliminated in the manner

described below.

  When the crank 28 is turned in the direction of arrow B, the lateral surface of the notched portion 23 is in contact with the lateral surface of the association projection 24, in the state shown in FIG. 13 and in the Figure 14. Then, when the crank 28 is released by the user and that simultaneously the rotation of the crank 23 is interrupted, the crank 28 rotates in the direction of the arrow A shown in Figure 8, due to the force of return of the helical spring 25, and it returns to the state shown in FIG. 9 and in FIG. 10,

  passing through the state shown in Figures 11 and 12.

  In the state shown in FIGS. 11 and 12, neither the first thrust projection 65 nor the second thrust projection 66 is introduced between the bottom surface 22a or 22b of the association member 22 and the second surface side 8 of the drum 4. For this reason, the drum 4 can move in the

  direction of arrow P over a height h. As a result, the relaxation

  chement or the permanent elongation produced in the son 32 and 33 is easily eliminated, thanks to the free movement of the snap teeth 7 and 12, by means of the operation of the spiral spring 19, passing from the state shown on the

  Figures 13 and 14 in the state shown in Figures 9 and 10.

  As a torque generating means between the drum 4 and the ratchet plate 5, in order to produce a free movement, it is preferably possible to use for example a spiral spring

  19 as shown in FIG. 8.

  As shown in FIG. 8, the spiral spring 19 having one end 20 introduced into the first engagement groove 17 of the boss 16 of the ratchet plate 5 and having

  its other end 21 introduced into the second engagement groove

  Gement 18 of the internal peripheral surface of the second boot 2, is preferably used, because the size of the spiral spring 19 is not limited by the size of the drum 4. The latching member of the present invention is not limited to the ratchet plate 5. As shown in FIG. 15, it is possible to use, as a latching member, a ratchet drum 4a, having a configuration similar to that of the drum 4, and capable of winding the second wire 33

  around its outer peripheral surface.

  In addition, as shown in FIG. 16, a ratchet plate 5, having a small cylindrical projection 5b

  which is contained in the drum 4 and which is capable of winding

  the end part of the second wire around its surface

  device, can be used as a latching member.

  Although the direction of the relative torque between the drum 4 and the association member 22, which is dfi the elastic member (for example the coil spring 25 shown in Figure 10) is not limited, the direction of the torque dQ to the elastic member is preferably the direction in which the drum 4 is rotated in the direction of the grip of the latching toothing 7 with the latching toothing 12,

  as shown in Figure 8 or Figures 9 A 14.

  In this way, immediately after the crank 28 is

  turned in the free movement direction of the enclosure teeth

  quetting 7 and 12, the association member 22 is rotated by the helical spring 25. Thus, the loosening and permanent elongation of the wires can be eliminated from

  regularly and without jerks. The drive device according to the present invention can be

  used not only in the window regulator with an inverted J shape, as shown

  in Figure 3, but also in another type of regulation

  window guard, for example as shown in the figures

17 and 18.

  In the window regulator shown in FIG. 17, a drive device 48 and a guide rail 45 are mounted separately on a door of a motor car, or of a similar vehicle. Between the drive member 48 and the guide rail 45, wires 32 and 33 are stretched in a triangular shape. In the window regulator of FIG. 18, two wires 32 and 33 are used which are slidably mounted and guided in external envelopes 35 and 38, and which are

  arranged in a triangular shape.

  In FIG. 19, the references 1 and 2 respectively designate a first shoemaker and a second housing. An overall case consists of the first case 1 and the second case 2. The whole case contains a member

  rotary drive 70 and supports the latter in rotation.

  The drive member 70 consists of a shaft 3 and a

  association member 22 of cup shape, extending radially

  Lement from the shaft 3. The association member 22, for example, can be attached to the shaft by welding. The association organ 22 has a fan-shaped scalloped part

  23 along its cylindrical peripheral part.

  A drum 4 is rotatably mounted on the shaft 3 to wind wires 32 and 33. The drum 4 is adjacent to the association member 22. The drum 4 has an association projection 24 capable of cooperating with the part indented 23 of the association member 22, with a certain play in the direction of rotation. Association projection 24 has a section

transverse fan.

  As shown in Figure 21, a central part

  trale of the drum 4 has a first bore 71 capable of being in direct contact with the shaft 3, and a second bore 72 having a diameter which is greater than the diameter of the shaft 3. The second bore 72 is coaxial with the first 71 The introduction of the shaft 3 into the bores 71 and 72 of the drum 4 delimits a cylindrical space 73. A helical spring 25 is mounted in the cylindrical space 73, and the two ends 25a and 25b of the helical spring 25 are engaged respectively in the association member 22 and in the drum 4. In this case, the helical spring 25 has received a torsional deformation, so that the helical spring 25 recalls the drum 4 in the direction of the arrow B, c that is to say in the direction of free movement of the snap teeth 7 and 12.

  In addition, the coil spring 25 recalls preferably

  the drum 4, which is movable in the axial direction, towards

the ratchet plate 5.

  In addition, in FIG. 19, the reference 7 designates a first latching toothing formed on the other lateral surface of the drum 4, and the reference 5 designates a ratchet plate having a second latching toothing 12 capable of coming into contact. taken with the first latching toothing 7. The ratchet plate 5 is recalled in such a direction that free movement occurs between the first and second latching toothing 7 and 12, that is to say direction of arrow A in FIG. 19. The spiral spring 19 has a

  end engaged in the second case 2 and the other end

  mite is engaged in a boss 16 on the ratchet plate 5.

  The ratchet plate has an engagement part 14 capable of accommodating a wire end 13 of a second wire 33. A wire end 9 of a first wire 32 is engaged and retained in an engagement part 10 provided in the

drum 4.

  The ratchet plate 5, the first and the second

  snap teeth 7 and 12 and spiral spring 19 cons-

  are a mechanism for adjusting the tension of the threads. The

  ratchet plate 5 and the second shoemaker 2 define a comparison

  timent intended to contain the spiral spring 19.

  If the crank 28 shown in FIG. 19 does not receive a torque, the association member 22 is returned in the direction of the arrow A by means of the spring

  helical 25, as shown in Figures 20 and 21.

  Thus, a lateral surface 23a of the indented part 23 always recalls a lateral surface 24a of the projection

  association 24 which faces the lateral surface 23a.

  The drum 4 itself can hardly be driven in rotation, because the drum 4 is connected to the window pane

  (for example marked at 100 in FIG. 24) via the

middle of wires 32 and 33.

  Consequently, the shaft 3 and the crank 28 do not turn

  not against the drum 4. This eliminates all

crank shake 28.

  When the crank 28, as shown in FIG. 19, is turned in the direction of arrow B, the association member 22 turns against the restoring force of the helical spring 25, over the range permitted by the game, the drum 4 being fixed. Then, the other lateral surface 23b of the indented part 23 pushes the other lateral surface of the association projection 24. As a result, the drum 4 can rotate. When the rotation operation is completed, the association member 22 returns to the state shown

  in Figure 20 and in Figure 21.

  When the crank 28 shown in Figure 19 is rotated in the direction of arrow A, from the state shown in Figure 20 and in Figure 21, the drum is directly rotated in the direction of the arrow

  A, because the lateral surface 23a on one side of the asso-

  ciation 23 is previously in contact with a surface

  lateral 24a of the association projection 24. In the arrangement

  drive tif according to the invention, a tip 31 of the braking spring 29 is introduced between a lateral surface 23a of the notched part 23 and a lateral surface 24a of the association projection 24, without play in the state shown on FIG. 20 and in FIG. 21. On the other hand, there is a certain clearance between the other lateral surface 23b of the part

  indented 23 and the other lateral surface of the associated projection

  ciation 24. Consequently, the unlocking operation

  and the locking operation can take place normally.

  The helical spring used in the drive device according to the present invention can be used -5 for any drive device having a drum and u. drive member which are associated with each other with a certain play in the direction of rotation. For example, the coil spring can be easily used in a prior art drive shown

in Figure 25.

  Regarding the drive device shown in Figure 25, the same spring as the coil spring shown in Figure 19 can be mounted between

  a drum 108a and an association organ 117.

  In drives equipped with a mechanism capable of automatically regulating the tension of

  wires by means of snap teeth, such as

  drive components shown in FIGS. 19 or 25, the helical spring 25 of the drive device according to the present invention also behaves like an elastic member which axially resembles a snap-to -othing toothing towards the other snap-fitting toothing, of so that the two sets of latching teeth strongly interlock. As a result, the coil spring can be used in place of a conventional washer

  wavy 121 as shown in Figure 25.

  As described above, the mechanism for preventing the crank from being shaken and shaken can be used in different cable drives or in different window regulators, for example the window regulators shown

in Figures 17 and 18.

  As described above, the drive device

  according to the invention has the effect that the relaxation and the lengthening

  permanent wire management can be eliminated, that the tension

  The wire is kept within a suitable range because the freewheeling phenomenon is suppressed, and the jerking and shaking of the crank are suppressed.

stre way.

  Of course, various modifications can be made by those skilled in the art to the devices which have just been described only by way of nonlimiting examples.

  without departing from the scope of the invention.

Claims (13)

  1. Drive device used in a regulation   window guard (39), characterized in that it comprises (a) a shoemaker (1, 2), (b) a drum (4) rotatably mounted in said shovel (1,2) and having a first lateral surface (6) which has a first latching toothing (7), as well as a second lateral surface (8) having a first engagement part (10) intended to retain a first end (9) of wire, and a surface device acting as a winding surface (36), (c) a ratchet plate (5) adjacent to and coaxial with said drum (4) and having a surface (11) having a second latching toothing (12 ) intended to come into engagement with said first latching toothing (7) of said drum (4) and a second engagement part (14) intended to retain a second end (13) of wire, (d) a spiral spring ( 19) having one end (20) engaged in said ratchet plate (5) and having its other   end (21) engaged in said case (1,2), and rappe-   lant said ratchet plate (5) in such a direction that said first latching teeth (7) and said second latching teeth (12) are moved freely, (e) an elastic member (25) axially recalling said drum ( 4) towards said ratchet plate (5), and (f) a shaft (3) intended to drive in rotation   said drum (4) by engagement with said drum.   2. Drive device according to claim 1, characterized in that said return direction of said spiral spring (19) corresponds to a lifting direction of a window window (G).   3. Drive device according to claim 1, characterized in that the return torque of said spiral spring (19) is greater than the couple of free movement of said first latching toothing (7) and said   second click teeth (12).   4 Drive device according to claim 1, characterized in that said second engagement part (14) of said ratchet plate (5) is located outside of said second latching toothing (12) in the radial direction . 5. Drive device according to claim 1, characterized in that said second engagement portion (54) of said ratchet plate (53) is located inside said second latching toothing (12) in the direction radial. 6. Drive device according to claim, characterized in that said first lateral surface of said drum (56) has a cylindrical groove (57) around the axis of said drum (56) having a helical winding groove (62) extending from said peripheral surface   said drum (56) adjacent to said first side surface   rale, towards said cylindrical groove (57), said ratchet plate (58) having a cylindrical projection (59) intended to be introduced into said cylindrical groove (57), said cylindrical projection (59) having said second engagement part ( 60), and a winding surface is provided   on a peripheral surface (61) of said cylindrical projection drique (59).   7. Drive device according to claim 1, characterized in that the diameter of said spiral spring (19) in the mounting configuration in said housing (1,2)   is greater than the diameter of said drum (4).   8. Drive device used in a regulation   window guard (48), characterized in that it comprises: (a) a boot (1, 2), (b) a drive member (70) comprising a shaft (3) rotatably mounted in said boot ( 1,2) and an organ   association (22) fixed to said shaft (3), said association member   ciation (22) extending from said shaft (3) in the radial direction and having at least one notched part (23) along a peripheral edge of said association member (22), (c) a drum (4 ) mounted in said case (1,2), adjacent to said association member (22), coaxial with said shaft (3), rotatable around said shaft (3), axially movable along said shaft (3), and having a projection association (24), said association projection (24) being mounted on a first lateral surface of said drum (4) which faces said association member (22), and being intended to cooDerate with said indented part (23 ), with a certain play in the direction of rotation, and having a first latching toothing (7) on a second lateral surface of said drum (4) which is opposite to said first lateral surface of said drum (4), (d) a latching member (5), mounted in said case (1,2), adjacent to said drum (4), coaxial with said shaft (3), rotatable with said shaft (3), and presents a second latching toothing (12) on a first side surface of said latching member (5) which faces said drum (4), said second latching toothing (12) being intended to engage said first latching toothing (7), (e) a spiral spring (19) disposed between said latching member (5) and said case (1,2), and recalling said latching member (5) in the direction of free movement of said first latching toothing (7) and said second latching toothing (12), (f) an elastic member (25) located between said drum (4) and said association member (22) of so as to recall said association member (22) in the direction of rotation, (g) a first wire (32), having one end (9) engaged in said drum (4) and a second wire (33) having one end (13) engaged in said latching member (5), and (h) a first thrust projection (65) and a second thrust projection (66), which are mounted on both cabled from the bottom of said association projection (24), and q5 which are intended to be introduced between bottom surfaces (22a, 22b) of said association member (22), and said   first side surface of the drum (4), respectively.   9. Drive device according to claim 8, characterized in that said elastic member (25) recalls said drum (4) and said association member (22) in the direction of free movement of said two interlocking teeth. (7.12).   10. Drive device according to claim 8, characterized in that said latching member is a ratchet plate (5).   11. Drive device according to claim 8, characterized in that said latching member is a ratchet drum (4a) capable of winding said second wire (33)   on a peripheral surface of said ratchet drum (4a).   12. Drive device used in a regulation   window guard (48), characterized in that it comprises: (a) a shoemaker (1, 2), (b) a drive member (70) comprising a shaft (3) rotatably mounted in said housing (1 , 2), and an organ   association (22) fixed to said shaft (3), said association member   ciation (22) extending in radial direction from said shaft (3) and having at least one notched part (23) along a peripheral edge of said association member (22), (c) a drum. (4), mounted in said case (1,2), adjacent to said association member (22), coaxial with said shaft (3) and rotatable around the latter, and having an association projection (24) which is mounted on a first surface   lateral of said drum (4) facing said associated member   tion (22), and intended to cooperate with said indented part (23), with a certain play in the direction of rotation, and (d) an elastic member (25) recalling said association member (22) in the direction of rotation, by engagement of one end (25b) of said elastic member (25) with said drum (4) and by engagement of the other end (25a) of said   elastic member (25) with said drive member (70).   13. Drive device according to claim 12, characterized in that said elastic member is a spring helical (25).