CH618246A5 - Speed varying device and its use - Google Patents

Abstract

The device consists of a drive component (10) supporting radially movable jaws (11) returned inwards by a spring. These jaws, actuated by associated flyweights (19) may bear on the cylindrical parts of two inner (4) or outer (5) pulleys, depending on the magnitude of the centrifugal acceleration to which the flyweights are subjected, thus bringing about, for a given speed, the disengagement of one pulley and the engagement of the other. However, the flyweights comprise a finger (26) interacting with a locking component (21) which prevents the flyweights from moving radially outwards when they revolve in a given direction. Thus, when this device is associated with a two-speed electric motor, it makes it possible to obtain three different speeds, the middle speed and the high speed being obtained in different rotational directions. This device may be used in a washing machine to give two spin speeds one of which is very fast. <IMAGE>

Description

The invention relates to a speed variator device; it also relates to the use of this variator in a washing machine provided with an electric motor with two speeds and direction of rotation.

A washing and spinning machine requires washing drum drive means capable of providing at least two speeds to it: a slow speed for washing, a faster speed for spinning.

Up to now, the most commonly used motor means has been the single-phase two-pole asynchronous motor.

2-pole, 12-pole, 2-pole, 16-pole, 2-pole, 18-pole motors are used widely, which give washing drum speeds between 50 and 55 rpm, and spin speeds, respectively. of 350,450 and 500 rpm.

The market trend is moving towards increasingly high spin performance; spin speeds of 850 rpm are required. To reach these speeds, various solutions are already used; one of these consists in using a 2-pole-32 pole motor, another consists in using a 2-pole-4 pole motor with which a reducing gear train, a free wheel and a centrifugal clutch are associated.

The first of the solutions cited has its weight and considerable bulk, as well as a very high price.

The second of the solutions cited, in addition to its relatively high price, is a delicate mechanism which requires multiple precautions in terms of programming to avoid false operations harmful to the device.

A third solution has already been proposed, bringing together a 2-pole -16 pole motor (of a common type) and a relatively simple mechanical variator, approximately doubling the transmission ratio for high speed. According to this solution, which will be illustrated moreover in more detail in conjunction with FIGS. 1 to 6, the command which brings the drive either to the state where it provides the small transmission ratio, or to the state where it provides the large transmission ratio, is given by the very speed of the drive shaft. drive input; the high steady state speed, by operating 2 poles, ensures the high mechanical transmission ratio, while the approximately eight times lower steady state speed, by operating 16 poles, ensures the low transmission ratio. In this way, there is a ratio of 1 to 32 between the speeds of rotation of the drum for washing and rotation of the drum for spinning.

With this known device, however, there is no possibility of having the high speed (2 pole operation) of the motor and the low mechanical transmission ratio.

However, in the complete washing process, it is desirable to have intermediate spins less powerful than the final spin and for which a speed of approximately 400 to 500 rpm is suitable. The known device in question solved this problem by brief pulses (about 5 s) of high speed control, so that, due to the inertia of the drum, the speed at the end of this pulse was only one fraction of the high speed in steady state. However, this speed reached at the end of the pulse varied as a function of the load and, for several successive pulses, it increased each time due to the reduction in inertia due to the departure of the water.

A solution allowing to have two spin speeds, one as high as possible (around 850 rpm) for the final spin and the other approximately half the speed for the spin. intermediate rages, and this in a steady state not playing on questions of inertia of the drum, would therefore be highly desirable. However, the device known from the prior art, with which a high speed of the engine automatically and certainly engages the high mechanical transmission ratio, did not allow such an intermediate spin speed to be obtained.

Furthermore, the drive control system by the very speed of the input shaft thereof, that is to say the speed of the motor, to the exclusion of any other command given from the outside. to the variator, brought advantages of simplicity and mechanical robustness which there can be no question of giving up.

The object of the present invention is to provide a speed variator device which, controlled by a two-speed motor, provides the two above-mentioned performances, that is to say, on the one hand, delivery, at will, of '' a washing speed (low), an intermediate spin speed (quite high), and a final spin speed (very high) and, on the other hand, control of the change of transmission ratio mechanical performed

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only in response to the speed of the input shaft, without other means of control from outside the drive. It goes without saying that the variator that the invention aims to provide must also be simple and robust, of advantageous manufacture.

According to the invention, this object is achieved by the presence of the characters set out in the appended claim 1. Embodiments further having, respectively, the characteristics set out in claims 2 and 3 make it possible to achieve this object under particularly advantageous conditions. The specific use of the drive as claimed in claim 4 takes advantage of these advantages.

The appended drawing illustrates, by way of example and compared with the prior art, an embodiment of the object of the invention used in a washing machine, in which:

fig. 1 and 2 represent an overall front and side view of a horizontal drum washing machine,

fig. 3 represents the cross section of a variator device of a known type, but the prior consideration of which is useful for a better understanding of the particular design proposed by the invention,

fig. 4 shows the longitudinal sections of the device along the axes A and B of the section of FIG. 3,

fig. 5 shows a graph representing the curves of the torques as a function of the speed of the motor, with a device like that of FIG. 3,

fig. 6 represents a speed-time diagram of the cycle of a washing machine in its final spin phase,

fig. 7,8,9 and 10 represent an embodiment of the variator device according to the invention,

fig. 11 represents a graph representing the curves of the torques as a function of the speed of the motor in the case of a device according to FIGS. 7-10,

fig. 12 shows a diagram relating to the wringing and final backwashing operations of a washing machine equipped with the device according to FIGS. 7 to 10.

We see in fig. 1 and 2, the variator 1 carried by the shaft 3 of a motor 2 with two polarities, a 2-pole motor -16 poles for example.

The variator comprises two pulleys 4 and 5 in the grooves of which two belts 6 and 7 take place, said belts coming to engage in the grooves of two other pulleys 8 and 9 which are integral or of the same piece. The pulleys 8 and 9 are in turn secured to an axis of the washing drum, the latter being enclosed in a tank. Figs. 1 and 2 represent a machine with two bearings, therefore opening from above; It goes without saying that the invention is also valid in the case of a machine with a bearing, therefore with a front window. The diameters of the pulleys 4,5,8 and 9 and the distance between the motor and the drum are preferably chosen so that the belts have identical lengths.

The description and the explanation of operation are made in the case of a 2-pole -16 pole motor, but the invention also accommodates 2-12 pole, 2-18 pole or other motors.

When the motor 2 is supplied on 16 poles, it rotates at a speed of the order of 350 rpm. At this time, the pulley 4 is secured to the motor shaft and the idler pulley 5 relative to the same motor axis. Let D4 be the diameter of the pulley 4 and D8 the diameter of the pulley 8. The drum speed in rpm, at this time, will be:

350-nl

D4 and D8 being chosen so that the drum speed is substantially equal to 50 rpm.

When the motor 2 is supplied on 2 poles, it rotates at a speed of the order of 2950 rpm. By means of the variator, the details of which are given below, the pulley 4 becomes mad on the motor shaft 3, while the pulley 5 becomes integral with said motor axis. Let D5 be the diameter of the pulley 5 and D9 the diameter of the pulley 9. At this time, the speed of the drum will be:

2950-gf

The invention is of interest only if c? is greater than sf, i.e. if the spin speed is greater than:

2950- {55

otherwise it would be useless to use two pulley couples and a variator to switch from one to the other.

In fig. 3 and 4, representing sections of a known variator, we see a drive part 10 keyed onto the motor shaft 3. Two jaws 11 are articulated by axes 13 on this drive part 10; these jaws are provided with suitable friction materials both on their internal edge and on their external edge. These friction materials play an important role in the operation of the machine, as will be explained later.

- the right part of fig. 3 shows a jaw that is not stressed by centrifugal force;

- the left part of fig. 3 shows a jaw stressed by centrifugal force.

In the absence of centrifugal stress, the two jaws 11 are applied externally to a cylindrical part of the pulley 4, this pulley being in a suitable material with respect to friction, by means of two helical traction springs 12 , which are supported, on the one hand, at the end of a jaw and, on the other hand, on the other jaw at a point close to its articulation. The pulley 4 is capable of relative speed with respect to the motor shaft 3 thanks to a ball bearing 14 (or other); the pulley 5 is extended by a cylindrical part on which are likely to come to bear internally the parts of friction material located on the outer edge of the jaws 11. The pulley 5 is also made of material suitable for friction; it is integral with a housing 15, which can freely swirl on the shaft 3 thanks to two bearings 16 and 17. All of the parts 14, 10 and 16 are stacked on the shaft 3 and held by a screw 18. Note that the housing 15 which is integral with the pulley 5 (corresponding to the high speed of the drum) is external to the entire system.

The operation is as follows: when the motor turns on the highest polarity (16 poles for example, therefore 350 rpm), the centrifugal force exerted on the jaws 11 is much weaker than the force of the springs. The springs are determined so that the drive part 10 and the jaws transmit without slipping the engine torque to the pulley 4 which itself transmits it to the drum.

When the 16-pole winding is cut off from its supply and the 2-pole winding is supplied, the motor rotor increases its speed until the centrifugal forces exerted on the jaws 11 cancel the effect of the springs; at this instant, the two jaws are applied to the cylindrical part of the pulley 5 and the engine torque is transmitted to the drum by the latter.

It is possible, when the motor is running with its 2-pole winding supplied, to suddenly cut off its power supply and to supply the 16-pole winding in the same direction of rotation as that of the 2-pole winding; it follows an extremely energetic braking which is transmitted to the drum via the pulley 5, then the pulley 4.

It will be noted that the torque transmitted by the jaws is greater if the tangential friction force creates a torque which tends to apply the jaw to the cylindrical part of one of the two pulleys, this torque being counted from the axis d joint of the jaws.

Fig. 5 is a graph which represents the curves of the torques as a function of the engine speed. Compared to fig. 3, the spin direction is counterclockwise; for washing, the motor rotates alternately in one direction, then in the other:

- curve A is the curve of the motor torque as a function of the speed on 16-pole winding;

- curve B is the curve of the motor torque on 2-pole winding;

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- Curve C is the curve of the accelerating torque transmissible by the jaws 11 to the pulley 4;

- the curve D is the curve of the accelerating torque transmissible by the jaws 11 to the pulley 5;

- The curve E is the curve of the braking torque transmissible by the jaws 11 to the pulley 5;

- Curve F is the curve of the braking torque transmissible by the jaws 11 to the pulley 4, or the acceleration torque clockwise;

- point a is the operating point of the motor on 16 poles,

- point b is the point of intersection of C and B,

- point c is the start of detachment of the jaws on the pulley 4,

- point d is the start of contact of the jaws with the pulley 5,

- point e is the intersection of D and B,

- point f is the operating point under operating conditions on 2 poles.

When the motor operates on 16 poles, the transmissible torque of curves C and F is always greater than the motor torque of curve A; therefore, the pulley 4 rotates at the speed of the motor (pointa).

When the motor is powered on 2 poles, it increases its speed, the jaws are stressed by the centrifugal force which applies to them. The drum is accelerated via the pulley 4 with the engine torque from the origin to point b, i.e. around 1400 rpm, which corresponds to a drum speed of 220 t / min. In the meantime, the critical speed of the suspension, which is around 150 rpm (1000 rpm engine) on the drum, has been exceeded with a torque on the drum which corresponds to the engine torque multiplied by nf, therefore a higher torque. than that which would correspond to the multiplication of the engine torque by the ratio §§. This fact leads to a reduction in the amplitudes of the tank at the critical speed.

From point b, the transmissible torque becomes less than the engine torque, hence sliding of the pulley 4 relative to the jaws. After point c, the effects of centrifugal force on the jaws are greater than the effect of the springs, the jaws leaving the pulley 4. The increase in speed between point c and point d is necessary to overcome the increase of the force of the springs due to their elongation. At point d, the jaws make contact with the pulley 5, the latter rotating at a speed which is at least that of the motor at point b multiplied by the ratio dI'UI which is less than 1. Up to point c, the torque transmitted to the pulley 5 is less than the engine torque. At point d, the speed of the motor remains stable at maximum torque, throughout the acceleration period during which the speed of 5 remains lower than that of the motor. The torque transmitted by the jaws at 5 is the maximum engine torque. The acceleration torque to the drum is then that of the engine multiplied by nf. At the end of the slide, when 5 and 11 rotate at the same speed, the motor accelerates again, driving 5, and comes to be placed at point f which corresponds to the speed of the speed.

It will be noted that the passage from the disengagement of the pulley 4 to the clutch of the pulley 5 is not instantaneous. However, this delay is very short because, when the two pulleys are disengaged, the free motor comes very quickly to its new speed, both in acceleration and in braking.

During braking caused by cutting off the power supply to the 2-pole winding, and energizing the 16-pole winding, the drum decelerates according to a similar process, but opposite to that described above.

The advantage of this device has already been reported to be the rapid crossing of the critical speed of the drum, but it is also remarkable for its braking qualities. Indeed, the jaws, on their parts which come into contact with the cylindrical parts of the pulleys, are coated with a special material similar to that of drum brakes. Moreover, the cylindrical part of the pulley 5 of large diameter is external to the entire variator, and exposed to air, which promotes its cooling. The outside of the drive (or housing) acts as a brake drum. However, this outer pulley is the one which is engaged when the drum rotates at its highest speed, it is therefore the one which will have to absorb, during braking, the greatest kinetic energy.

These qualities of the variator are applied in the definition of the washing cycle of the washing machine. The fact of being able to brake vigorously and frequently is used to provide for a large number of high speed spin sequences, cut with backwashing at low speed. This is illustrated in fig. 6 which represents a diagram of the drum speeds as a function of time during the final spin operations. The programmer used in the example includes a step-by-step mechanism with a 2-minute delay. The times given are purely indicative.

Zone P is the emptying of the water contained in the tank; at this time, the drum rotates alternately in one direction and in the other, with a stopping time between each reversal.

Zone Q is a pulse wringing and braking backwashing zone; its purpose is to purge most of the water contained in the laundry and to ensure that it is cleaned before the final spin. It has a certain number of pulses (4 in fig. 6) each of which is made up of the following operations: rotation of the drum counterclockwise at 50 rpm for 4 s, then control of the 2-pole motor winding for 5 s counterclockwise, the top speed obviously being a function of the total inertia of the system, inertia which decreases as the water contained in the linen is removed; after 5 s, the 2-pole winding is cut and, at the same time, the 16-pole winding is energized counterclockwise; the braking thus obtained brutally brings the drum back to 50 rpm and begins the backwashing of the laundry, which is completed by a brief counterclockwise rotation, then a stop time of 3 s, then an hourly rotation of 12 s, then a time stop

Zone R is the final spin zone proper; the drum rotates at a high speed counterclockwise (850 rpm for example), this spinning being itself completed by a final braking already described.

Zone S is the final backwash zone which comprises, for several minutes, an alternating rotation at 50 rpm of the drum.

The known variator which has just been described, operating in conjunction with a two-speed 2-pole-16-pole motor, provides, in a simple manner, two permanent speeds of drum speed, one at 50 rpm and the other approximately at 800 to 850 rpm. On the other hand, it cannot provide (other than in a transient manner) under the drive at one or the other of the two motor speeds, a high intermediate output speed, of the order of 400 to 500 rpm, for intermediate spins. The embodiment of the particular design proposed which will now be described in conjunction with FIGS. 7 and following makes it possible to have three speeds instead of two, the average speed (intermediate spin) and the high speed (final spin) being obtained in different directions of rotation.

It will first be noted that when the pulley 4 is driven without sliding by the jaws 11, therefore at the speed of the motor, if N is its speed, the speed of the pulley 5 will be:

1M.54.D9 ■ N D8 D5

due to the double transmission. As §f is smaller than §§, the speed of the pulley 5 will always be less than N. In other words, whatever the direction of rotation of the motor, the pulley 5 and its housing are rotated relative to the drive part 10 supporting the jaws, opposite to the direction of rotation of the motor.

Figs. 7,8 and 9 give sections of the device according to this embodiment:

- fig. 7 right along plane A of fig. 8 and fig. 7 left according to plan B,

- fig. 8 right along plane C of fig. 7 and fig. 8 left according to

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plane D, the engine turning counterclockwise (indicated by the arrow),

- fig. 9 gives the same representations as there fig. 8 but with the engine running clockwise (indicated by the arrow).

We find in these figures, under the same references, certain constituents identical to those described in connection with FIGS. 3 and 4; the following differences however distinguish the particular embodiment according to figs. 7 to 9.

While, in the known device described above, the jaws 11 had an appropriate mass vis-à-vis the centrifugal force to overcome the resistance of their associated springs 12 and move away from the pulley 4 by resting on the pulley 5 , here the jaws 11 have a much smaller mass (for example of aluminum alloy), sufficiently low compared to the force of the springs 12 so that, at the maximum speed of the motor (of the jaws), the centrifugal force cannot take off these jaws of the pulley 4. Thus, the pulley 4 is never disengaged, regardless of the speed of the motor.

Weights 19 are articulated on the same axis as the jaws 11; they are brought back towards the center by springs

20 hung, on the one hand, at the end of the counterweights and, on the other hand, at a point close to the articulation of the symmetrical counterweight, in a manner analogous to the fixing of the springs 12, opposite screw jaws 11. Unlike the jaws, these weights 19 have a much larger mass relative to the force of their spring 20, as will be explained later.

A locking piece 21 can rotate relative to the housing 15, therefore relative to the pulley 5. This piece 21 swirls between two friction pieces 22 and 23.

The piece 22 provides radial and axial guidance of the locking piece 21. The piece 23 provides axial guidance of the piece 21 while transmitting the axial force of a weak spring 24, which spring is immobilized axially in a groove of the hub of the housing 15. The part 21 therefore tends to be driven by the housing 15 with a low friction torque. The counterweights 19 comprise a finger 25, which can rest on the internal part of the jaws 11 or their external part, and a finger 26 which engages in a slot 27 in the locking piece 21.

Fig. 10 is a separate end view of the locking piece

21 which shows the detail of the lights 27 which it comprises. We note in particular the parts 28 having a small radial dimension and the parts 29 having a strong radial clearance, each with their angular stops.

The operation is as follows. Fig. 8 is a representation of the device, the engine rotating at 350 rpm counterclockwise. As has been said above, the jaw assembly with more weights rotates faster than the housing 15 and the pulley 5; the fingers 26 come into contact with the part 21 and engage in the part of the lumen of this part which has a small radial dimension. The fingers 25, due to the action of the springs 20, rest on an internal face of the jaws 11. The driving torque is then transmitted by the action of the springs 12 and 20.

When the 2-pole part of the motor is supplied in a counterclockwise direction and its speed increases, the weights 19 are stressed by centrifugal force; the springs 20 are calculated to immobilize the counterweights 19 at a speed slightly greater than 350 rpm, 500 rpm for example. At this time, the fingers 26 come to bear on the edge of the parts 28 of the openings 27 of the part 21; the fingers 25 leave the internal faces of the jaws 11, but are blocked in their course before coming into contact with the external faces of said jaws.

The mass of the jaws being small, they are weakly stressed by centrifugal force and the force of the springs 12 is sufficient to transmit without sliding to the drum, via the pulley 4, a speed: 2950-b | = 450 t / mn for example.

The return to speed 50 rpm can be effected by electric braking, as has been said previously.

Fig. 9 is a representation of the device, the engine rotating at 350 rpm clockwise. At this moment, the fingers 26 come to engage in the part 29 of the openings 27 of the part 21 which has a large radial clearance, and make the said part rotate relative to the housing 15.

When the 2-pole part of the motor is supplied clockwise and its speed increases, the weights 19 can move away freely from the center of the device by pivoting on their articulation and the fingers 25 come into contact with the external part of the jaws 11 which are therefore stressed by the centrifugal force applied to their own mass and to the mass of the flyweights.

The mass of the weights, added to that of the associated jaws, is such, relative to the force of the return springs 12 and 20, that the jaws 11 leave the pulley 4 to come to be applied to the pulley 5 when the engine reaches a predetermined speed.

The operation is then analogous to that indicated above with reference to FIG. 4, especially for braking.

There is shown fig. 11 the various torque-speed curves similar to those of FIG. 5. The curves G and H have been added thereto which correspond to the operation of the device when the motor turns counterclockwise, that is to say in the direction where the weights are prevented by the part 21 from coming to bear on the jaws 11 which thus remain applied to the pulley 4. The latter remains engaged until beyond the maximum speed of the motor,

and the torque it can transmit is at all times greater than that of the engine.

The position of the axes 13 of articulation of the jaws 11 (and the weights 19) is chosen so that, in the direction of clockwise rotation (corresponding to the clutch of the pulley 5 at high speed), the jaws in contact with the pulley 5 tend to brace themselves as a result of the friction torque applied to them during braking. Thus, in a machine with two spin speeds, the highest drum speed has the highest braking torque (curve G).

There is shown fig. 12, by way of example, a speed (V) time (t) diagram which relates to the wringing and final backwashing operations of a washing machine equipped with the variator device described, in accordance with the particular design proposed.

Zone T corresponds to the evacuation of the water contained in the tank; the drum rotates alternately in one direction then in the other; zone U is a medium speed spin zone (450 rpm for example). While the drum, and therefore the motor, rotates counterclockwise at low speed, the 16-pole part of the motor is de-energized and the 2-pole part is energized in the same counterclockwise direction, as has been said. previously; the spin speed is only 2950-§f; zone V corresponds to backwashing after spinning at 450 rpm; it begins with electric braking and continues with an alternating rotation period of 50 rpm; zone X corresponds to the final spin at high speed. While the motor rotates clockwise, its 16-pole part is cut and the 2-pole part is supplied clockwise and the spin speed is then equal to 2950-ni or about 850 rpm, as in the previous version; zone Y corresponds to the final backwashing period which begins with electric braking and ends with an alternating rotation at 50 rpm.

These results correspond well to the performances which one aimed to obtain by the particular design proposed. It will be noted that the variator device with three states proposed retains the simplicity of the analog variator device, but with only two states, which the prior art knew; it is just as compact, its entire mechanism being contained in a single sealed housing, the additional distinction necessary for control being found in the direction of rotation, in itself unimportant as to the quality of the spin.

On the other hand, as we said, in the machine with two spin speeds, that is to say with the variator with three speed states, the

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Braking torque is most effective at high speed, resulting in effective braking, but which is never violent.

It should also be noted that significant braking strokes can be given frequently, without prohibitive heating, because the pulley 5, integral with the housing, supports the highest braking energies and that this housing, then playing the role of drum brake, cools directly to the outside atmosphere.

Finally, the fact of fixing the moment of the change to the high speed ratio after the drum speed has exceeded the critical speed allows the drum to cross it with the maximum acceleration torque, that is to say in minimal time.

R

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Claims (4)

618,246 1. Speed variator device (1), intended to be fixed on the shaft of a two-speed electric motor (2), having on the one hand two internal (4) and external (5) pulleys, and on the other hand a drive part (10) supporting, between these pulleys, radially pivoting jaws (11), elastically biased towards the inner pulley (4) by springs (12), characterized in that the mass of the jaws and the pulling force of their return spring (12) is such that under the effect of centrifugal force, and without mechanical intervention of the other members of said device, these jaws remain applied against the internal pulley (4), whatever the speed of rotation of the drive part (10), and in that it comprises radially pivoting weights (19) provided with return springs (20) and, in each of them, two fingers (25,26 ) one of which (25) is engaged between the inner edge and the outer edge of the associated jaw and displacab the in the space between these edges, the own mass of the counterweight and the tensile force of its return springs being such that, in operation in cooperation with the associated jaw but without mechanical intervention of the other organs of this device and under the effect of centrifugal force, the counterweight (19) recalls the jaw (11) against the inner pulley (4) by pressing its finger (25) on the inner edge thereof, for a speed of rotation of the drive piece (10) less than a predetermined value, and applies this jaw (11) against the outer pulley (5) by pressing his finger on the outer edge of said jaw, for a speed of rotation of the piece upper drive (10) at this predetermined value, and a movable locking piece around the axis of rotation of the two pulleys (4,5) and having, for each counterweight (19), a light (27) which receives the second finger (26) of said counterweight (19) to prevent this counterweight from reaching its radial end of travel towards the outside for a rotation of the drive part in a given direction, and leaving said counterweight (19) free in its radial displacement for a rotation of the drive part in reverse. 2. Device according to claim 1, characterized in that the locking part (21) comprises, for each of the monkfish (19), a lumen (27) transversely divided into two parts, one of which has a width more radially larger than that of the other. 2 3. Device according to claim 1, characterized in that it comprises two friction parts (22,23) ensuring a framing of the locking part (21) and a spring (24) keeping them applied against the external pulley (5 ). 4. Use of the speed variator device according to claim 1 in a washing machine provided with an electric motor with two speeds and two directions of rotation, characterized in that the speed variator device is arranged to be actuated by this electric motor to provide, on the one hand, when the latter rotates in one direction of rotation, two operating speeds, one for washing and one for an average spin and, on the other hand, when the motor rotates in the other direction of rotation, a high speed of rotation for a deep spin.