JPS5912317B2 - Transmission for electric washing machine motor and electric washing machine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a transmission for a dehydrator of an electric washing machine, which is equipped with pole number switching, and an electric washing machine equipped with this transmission.

Electric washing machines and dehydrators require one drive that can provide at least two speeds.

The most widely used drive device in the past is a single-phase asynchronous pole-switching motor having two sets of magnetic poles.

Among them, the most widely used motors are 2/12 pole, 2
/16-pole and 2/18-pole motors rotate 50-55 revolutions per minute during washing and 350 revolutions per minute during spin-drying.
．． It is designed to rotate at speeds of 450 and 500 revolutions.

Market demand is trending toward higher speed dehydrators, and 8
A dehydrator speed of 50 rpm is required.

Various means are used to obtain such high rotational speeds.

One is to use a 2/32 pole motor, the other is to use a 2/4 pole motor with a reduction gear, a freewheel and a centrifugal clutch.

The disadvantage of the first motor is that it is large in weight, bulky, and very expensive.

In addition to being relatively expensive, the second motor requires great care to avoid incorrect operation of the machine in which it is used.

The object of the present invention is to provide a low cost, simple and robust transmission which is combined with a simple electrical controller and which provides different reduction ratios.

The transmission of the present invention is attached to the shaft of a two-speed motor, and is provided with two pulleys.

These pulleys are each mechanically coupled to one of the other two pulleys attached to the shaft to be driven.

The diameter ratios of the two pairs of pulleys connected in this way are different and correspond to the desired speeds obtained from the two types of rotational speeds of the drive shaft.

This transmission includes a drive section attached to a drive shaft, a first (inner) pulley that is freely attached to the drive shaft and has a cylindrical section, and a second (outer) pulley that is attached to the drive shaft and has a cylindrical section. The drive part, consisting of a pulley, supports at least one movable shoe that is movable in a radial direction relative to the drive part, the shoe being pushed radially towards the drive shaft by means of a resilient member and pushing the cylindrical part of the inner pulley. a section is disposed inside the drive section and radially faces at least a portion of the movable pulley, and the outer pulley is disposed outside the drive section and radially faces at least a portion of the movable shoe. It is designed to face.

As a result, when the rotational speed of the drive shaft is higher than the rotational speed at which the centrifugal force on the shoe is greater than the restraining force exerted by the elastic member, the shoe is moved away from the inner cylindrical portion and the outer cylindrical portion is moved. push, thereby releasing the first pulley and applying it to the second pulley.

When the motor is rotating at a low speed, the force applied by the elastic member of the shoe is greater than the centrifugal force, so the first pulley is applied and the second pulley is free.

As the rotational speed of the motor increases, its centrifugal force forces the shoe against the outer pulley, thereby engaging the outer pulley and releasing the inner pulley, leaving it free.

The reduction ratio (or increase ratio) of the first pulley pair is selected to provide the required low speed to the driven shaft, and the reduction ratio (or increase ratio) of the second pulley pair is selected to provide the required low speed to the driven shaft. Provides the required high speed rotation.

The speed reduction ratio (or speed increase ratio) of the second pulley pair is higher than that of the first pulley pair.

If this is not the case, it is easier to choose a motor with a small difference between low and high speeds, which eliminates the need for double pulleys or special latches.

It will be appreciated that this transmission operates similarly for both directions of rotation of the motor, unlike a transmission using a freewheel arrangement.

If this transmission is modified, three speeds can be obtained from the same device.

Intermediate speeds in this case are obtained by rotating in the opposite direction.

Therefore, the first speed is obtained from the low-speed rotating motor by a pulley pair with a small reduction ratio, the second speed is obtained from the high-speed rotating motor by a pulley pair with a low reduction ratio, and the third speed is obtained from the high-speed rotating motor by a pulley pair with a high ratio. Obtained by pair.

The first speed is available in both directions of rotation, the second speed is available only in one direction of rotation, and the third speed is available only in one opposite direction of rotation.

According to another feature of the invention, the above results provide the transmission with:
This is accomplished by the addition of at least one weight associated with each shoe and a fixing member that is carried by an outer pulley and mounted for rotation about the axis of the pulley, said weight being associated with the drive. The weights are mounted for radial movement with respect to the mating shoes, and each weight is pushed radially toward the drive shaft by a resilient member, and after being moved radially a predetermined distance, the weights are assembled. Pressed in one or the opposite direction against the mating shoes, said fixing member is coupled to the pulley by a friction mechanism, said fixing member having at least one angular stop for each direction of rotation and a respective weight. a radial stop for the drive, said angular stop also defining two angular positions relative to the drive by contacting a component attached to the drive, each angular position corresponding to one revolution of the pulley relative to the drive. , said radial stop corresponds to one of said two angular positions, and said radial stop engages each weight so that said fixing member is in that angular position. When in position, each weight is prevented from moving radially toward and contacting the associated shoe.

In this transmission, one pulley is disengaged and the other pulley is engaged at different speeds depending on the rotating direction of the drive shaft.

Hereinafter, the present invention will be described in detail with reference to the drawings.

In the figure, reference numeral 1 denotes a transmission, which is attached to the shaft of a pole number switching motor 2, such as a 2/16 pole motor.

Two pulleys 4 and 5 are attached to this transmission 1.

Belts 6.7 are respectively hung in the grooves of these pulleys.

These belts are hung over other pulleys 8, 9 which are integrally fixed to each other.

Pulleys 8 and 9 are fixed to the shaft of the drum of the washing machine.

This drum is housed inside the tank.

Although Figures 1 and 2 show a machine with two bearings, which is therefore of the open-topped type, it is clear that it can also be used with machines with just one bearing. In that case, this washing machine is provided with a front door.

The diameters of the pulleys 4, 5, 8, 9 and the distance between the motor axis and the drum axis are determined so that the belts have the same length.

The following explanation uses a 2/16 pole motor as an example;
The present invention is equally applicable to /12-pole motors, 2/18-pole motors, etc.

When the 16-pole winding of motor 2 is energized, the motor
Rotates at a speed of 50 rpll.

At the same time, pulley 4 is engaged with the drive shaft and pulley 5 is pulled away from the drive shaft.

If D4 is the diameter of pulley 4 and D8 is the diameter of pulley 8, then the number of rotations of the drum at this time is.

D4 and D8 are selected such that the drum rotation speed is approximately equal to 50 rpm.

When the two-pole winding of motor 2 is energized, motor 2 will be approximately 29
It rotates at a speed of 50 rl'.

The pulley 4 becomes free on the drive shaft 3 and the pulley 5 is engaged with the drive shaft 3 by a transmission which will be explained later.

If the diameter of pulley 5 is D5 and the diameter of pulley 9 is D9, then the number of rotations of the drum is as follows.

Benefits are obtained when D5/D9 is higher than D4/D8, i.e. when the rotation speed of the dehydrator is higher than, if this is not the case, in order to change from one pair of pulleys to the other. There is no advantage to using two pairs of pulleys and a transmission.

3 and 4 show a drive 10 which is keyed to one drive shaft 3. FIG.

Two shoes 11 are pivotally attached to this drive section 10.

A suitable friction material is applied to the inner and outer surfaces of the shoes.

These friction materials play an important role in the operation of this transmission.

The right side of FIG. 3 shows the shoe when no centrifugal force is applied, and the left side of FIG. 3 shows the shoe when centrifugal force is applied.

When no centrifugal thrust is applied, the two shoes 11 are moved by two coiled tension springs installed between one end of one shoe and near the pivot point of the other shoe. It is pressed against the outside of the cylindrical part of the pulley 4 (which is made of a suitable material from the point of view of friction).

The pulley 4 can rotate at a relative speed to the drive shaft 3 by means of a bearing 14 .

The pulley 5 extends into the cylindrical part.

A piece of friction material attached to the outer surface of the shoe 11 contacts the inner part of this cylindrical part.

The pulley 5 is also made of a suitable material from the point of view of friction.

This pulley 5 is fixed to a housing 15 that can freely rotate around the shaft 3 by two bearings 16 and 17.

The parts 14, 10, 16 are mounted on the shaft 3 in the order listed here, from top to bottom of the shaft.

These parts are then screwed together by screws 18. It is fixed at 3.

The housing 15, which is fixed to the pulley 5, is external to the entire mechanism.

The operation of this transmission will be explained next.

When the motor 2 rotates with a large number of poles (for example, 16 poles, therefore 350 rl1m), centrifugal force is applied to the shoe 11.

The force is much smaller than the force being applied by the springs 12.

The strength of these springs is such that the drive unit 10 and shoe 11 transmit torque to the pulley 4 without causing slippage, and the pulley 4
is determined to transmit torque to the drum.

When the 16-pole winding is de-energized and the 2-pole winding is energized, the motor speed increases until the centrifugal force on the shoe 11 becomes greater than the force of the spring 12.

When the centrifugal force becomes greater than the force of the spring 12, the two shoes 11 move outward.

- This pulley 5 transmits torque to the drum by pushing the cylindrical portion of the pulley 5.

When the motor 2 is rotating with the 2-pole windings energized, the current supplied to those windings is suddenly cut off, and the 16-pole winding is energized to continue rotating in the same direction as before. I can do it.

This results in a very strong braking action, which is transmitted via the pulley 5 to the drum.

If the tangential frictional force generates a torque that forces the shoe against the cylindrical portion of one of the pulleys, the torque transmitted by the shoe will be high and is measured from the shoe's inclination angle.

FIG. 5 is a graph showing the torque curve as a function of the speed at which the motor rotates.

With reference to FIG. 3, the direction of rotation of the dehydrator is counterclockwise, and for washing the motor alternates between one direction and the opposite direction.

Curve A shows the motor torque as a function of the rotation speed for a 16-pole motor, curve B shows the motor torque as a function of the rotation speed for a 2-pole motor, and curve C shows the motor torque as a function of the rotation speed for a 2-pole motor.
The acceleration torque curve that can be transmitted from the shoe 11 to the pulley 5, the curve E is the braking torque curve that can be transmitted from the shoe 11 to the pulley 5, and the curve F is the acceleration torque that can be transmitted from the shoe 11 to the pulley 5. Counterclockwise braking torque curve or acceleration torque curve that can be transmitted to the motor, point a is the operating point of the motor when operating with 16 poles, point b is the intersection of curves C and B, point C is the shoe 11
The point at which the shoe 1 begins to rise and separate from the pulley 4, point d, is the shoe 1.
Point e, where point 1 begins to come into contact with pulley 5, indicates the intersection of curve B and point f, and point f indicates the operating point of the motor when operating with two poles.

When the motor is operating with 16 poles, the transmittable torque represented by curves C and F is always higher than the motor torque represented by curve A.

Therefore, the pulley 4 rotates at the same speed as the motor (a
point).

When the motor 2 is operating with two poles, its rotational speed becomes high, and the shoe 11 receives thrust from the centrifugal force applied thereto.

The drum moves from the beginning to point b, i.e. about i4oorpm.
is accelerated by the motor torque transmitted via the pulley 4.

At the above rotation speed, the drum rotation speed is approximately 220 rpII.
becomes.

During the acceleration period, the critical speed of the drum suspension mechanism (approximately 1
5Or+''', the motor rotation speed at this time is approximately 1ooor
pm), and the torque transmitted to the drum at that time is the motor torque multiplied by D4/D8.

In other words, the torque at that time is the ratio of the motor torque to D5/
D is higher than the torque generated by multiplying by 9.

As a result, the amplitude of the tank at critical speed will be reduced.

Above point b, the transmittable torque is lower than the motor torque, so the pulley 4 slips with respect to the shoe 11.

After passing point C, the centrifugal force applied to the shoe 11 is greater than the force applied by the spring 12, and the shoe 11 separates from the pulley 4.

Between points C and d, the motor needs to rotate at a higher speed to overcome the increased force exerted by the spring due to its extension.

At point d, the shoe 11 contacts the pulley 5, and the pulley 5 is rotated at least at a ratio D4/D8XD9 to the motor rotation speed at point b.
It rotates at a rotation speed multiplied by /D5.

This ratio is less than 1.

Up to point C, the torque transmitted to the pulley 5 is lower than the motor torque.

At point 6, the rotational speed of the motor can be kept constant at the maximum torque during the entire acceleration period, during which the rotational speed of the pulley 5 is kept lower than the rotational speed of the motor.

The torque transmitted to the pulley 5 by the shoe 11 is the highest motor torque.

Therefore, the acceleration torque of the drum is D9 to the motor torque.
It is the torque multiplied by /D5.

At the end of the slippage, the pulley 5 and the shoe 11 are now rotating at the same speed, and the motor continues to accelerate until it reaches point f, which represents its steady speed.

It will be appreciated that the switching to disconnect pulley 4 and to engage pulley 5 does not occur instantaneously.

However, the switching time is very short, so when the two boobies are disconnected together, the unloaded motor reaches its new speed very quickly, both during acceleration and deceleration. .

When the 2-pole winding is de-energized and the 16-pole winding is energized and braked, the drum is sped up in a similar but reverse order as described above.

Having mentioned above the advantage of the transmission that the critical speed of the drum is passed very quickly, its damping characteristics are also worth noting.

In fact, the part of the shoe that contacts the cylindrical part of the pulley is lined with a special material similar to that used in drum brakes.

Furthermore, cooling of the pulley is supplemented because the large diameter cylindrical portion of the pulley 5 is outside the converter assembly and exposed to air.

The outer part (housing) of the converter performs the function of a brake drum.

Also, the outer pulley 5 is the pulley that is engaged when the drum is at its highest speed, and is therefore the pulley that is required to absorb the largest amount of kinetic energy during braking.

Those characteristics of the transmission of the invention are used in determining the wash cycle of the washing machine.

This strong damping ability is often used to combine multiple high-speed dewatering cycles with slow detangling cycles interposed between those dewaterings.

This state is shown in FIG. This figure shows a graph of the relationship between the drum rotation speed (2) and the time t during the final dewatering operation.

The programmer featured in this example includes a step-by-step mechanism with a timing cycle of two minutes.

This two minute timing cycle is purely exemplary.

Section P indicates the time for draining water in the tank.

During this time, the drum repeatedly rotates forward, stands still, and reverses.

Section Q is a section for rapidly accelerating dehydration and detangling by braking, the purpose of which is to expel most of the water contained in the laundry and to detangle the laundry before the final dehydration. It is.

This section includes a certain number (4 in FIG. 6) of speed jumps, and each speed jump includes the following actions.

The drum rotates counterclockwise at 50 rpm for 4 seconds,
The two-pole winding is then energized for 5 seconds to rotate the motor counterclockwise, the maximum speed being a function of the total inertia of the transmission, which inertia is reduced by the amount of water contained in the laundry. It decreases as time goes by.

After this 5 seconds have elapsed, the two-pole winding is de-energized,
At the same time, an excitation current is applied to the 16th winding in a direction that rotates the motor counterclockwise, and due to the resulting braking action, the rotational speed of the drum is increased to 5 Qrp in the counterclockwise direction.
It is suddenly lowered to m and begins untangling.

This disentangling action is completed with a brief counterclockwise rotation.

It then pauses for 3 seconds, rotates clockwise for 12 seconds, then comes to rest again.

Section R is the last dewatering section, during which the drum rotates counterclockwise at high speed, for example at 850 rl'').

This dewatering operation itself is completed by the final braking described above.

Section S is the last untangling section, and this section is 5Qr.
Consisting of alternating rotations at pH for several minutes.

A large number of repetitions of such rapidly repeated motions is only possible with a transmission capable of performing the specialized motions made possible by the features of the present invention.

In another embodiment described below, the transmission of the invention is capable of switching between three speeds, with the intermediate and highest speeds having different directions of rotation.

First, assuming that the pulley 4 is driven by the shoe 11 without slipping, that is, at the same speed as the motor, the number of rotations of the pulley 5 will be as follows, since there is double transmission, where N is the number of rotations of the motor.

Since D9/D5 is smaller than D8/D4, pulley 5 always rotates at a slower speed than N.

In other words, whatever the direction of rotation of the motor, the rotation transmitted to the pulley 5 and the housing, contacting the drive part 10 holding the shoe, is opposite to the direction of rotation of the motor. .

Figures 7.8.9 are cross-sectional views of such an embodiment of the transmission.

The right side portion of FIG. 7 is a cross section along plane A of FIG. 9, and the left side portion is a cross section along plane B of FIG. 9.

The right side portion of FIG. 8 is a cross section taken along plane C of FIG. 7, and the left side portion is a cross section taken along plane D of FIG. 7. The motor rotates in the direction of the arrow, that is, counterclockwise.

FIG. 9 is a diagram similar to FIG. 8, but in this diagram the motor rotates clockwise in the direction of the arrow.

In the transmission shown in Figures 3 and 4, centrifugal force causes the shoe 11 to
Shoe 1 resists the resistance force of spring 12 combined with
1 can move away from the pulley 4 and contact the shoe 5, whereas in the embodiments shown in FIGS. 7-9 the mass of the shoe 11 is much smaller (e.g. (made of aluminum alloy), this mass is small enough compared to the force exerted by the spring 12 that lifting the shoe 11 and pulling it away from the boot IJ 4 when the motor (and shoe) is at maximum speed is a centrifugal force. I can't do that.

Therefore, the pulley 4 never separates no matter what rotation speed the motor rotates.

Like the shoe 11, a weight 19 is pivotally mounted on the same shaft.

The weights are drawn toward the center by springs 20 attached to the ends of the weights and at points near the symmetrical weight pivot points.

Unlike the shoe 11, the mass of the weight 19 is the same as the spring 20.
much greater than the strength of

The fixing member 21 is rotatable relative to the housing 15 and thus to the pulley 5.

This fixed member 21 rotates between two friction pieces 22.23.

The friction piece 22 guides the fixing member 21 in the axial and radial directions.

The friction piece 23 transmits the axial force applied by the weak spring 24 fixed in the axial position in the groove of the bub of the housing 15, and guides the fixing member 21.

Therefore, the fixing member 21 can be moved together with the housing 15 with a low frictional torque.

The weight 19 has a spigot 25.

This spigot 25 can contact the inner or outer part of the shoe 11 and the spigot 26, the spigot 26 engaging in the opening 27 of the fixing member 21.

FIG. 10 is a plan view of the fixing member 21, showing in detail the opening 27 provided therein.

In particular, a region 28 with small radial dimensions and a region 29 with large radial dimensions are shown.

Each region includes angular stops.

The transmission of this embodiment operates as follows.

FIG. 8 shows a transmission in which the motor is rotating counterclockwise at a speed of 35 Orl'l.

As mentioned above, the shoe and weight assembly rotates at a higher speed than the housing 15, and the pulley 5 and spigot 26 contact the fixed member 21 and close the opening 27.
28.

Due to the action of the spring 20, the spigot 25 hits the inner surface of the shoe 11.

Therefore, the torque of the motor is transmitted by the action of springs 12 and 20.

When the two-pole windings of the motor are energized in a direction that causes the motor to rotate counterclockwise and the speed of the motor increases, the weight 19
centrifugal force is applied to

The spring 20 rotates at a rotation speed slightly higher than 350 rpm, for example 5Qrpln.

The strength is determined to keep the weight 19 stationary until it reaches .

When the motor reaches this speed, the spigot 26 comes into contact with the edge of the area 28 of the opening 27 of the fastening member 21.

Although the spigot 25 moves away from the inner surface of the shoe 11,
The movement is stopped before contacting the outer surface of the shoe 11.

Since the mass of the shoe 11 is small, the shoe 11 is not subject to much centrifugal force, and the force of the spring 12 moves the drum through the pulley 4, for example, 2.950X (D4/D8
)-45° is sufficient to drive without slippage.

The return to the speed of 5QrpH can be achieved by the electrical braking described above.

FIG. 9 shows the transmission when the motor is rotating clockwise at 350 rpm.

At this time, the spigot 26 is attached to the opening 2 of the fixing member 21.
7, and fixing member 21 is engaged with region 29 of housing 15.
rotate relative to.

When the two-pole windings of the motor are energized in a direction that causes the motor to rotate clockwise, the weights 19 move away from the center of the transmission by rotating about their pivot points;
The spigot 25 contacts the outer part of the shoe 11.

The shoe 11 is therefore subjected to a centrifugal force acting on its own mass and on the mass of the weight 19.

In accordance with a feature of the invention, the sum of the masses of weight 19 and its associated shoe, in relation to the force exerted by return springs 12 and 20, is such that when the motor reaches a predetermined speed, shoe 11 Move away from 4 and pulley 5
It can be set to a value that presses .

The subsequent operations are similar to those described with reference to FIG. 4, particularly with respect to braking.

Figure 11 shows the 5th section regarding torque and rotational speed.
A curve similar to that shown in the figure is shown.

The graph in FIG. 11 is obtained by adding curves G and H to the graph in FIG.

These curves G and H are obtained when the motor is rotating 0 times clockwise, that is, when the weight 19 is prevented from contacting the shoe 11 by the fixing member 21 and therefore remains pressed against the pulley 4. It relates to the operation of this transmission when rotating in the direction.

Since the pulley 4 remains in contact with the shoe 11 until the motor reaches and exceeds its maximum speed, the torque that the pulley 4 can transmit is always higher than the torque of the motor.

In accordance with the features of the invention, the shoe 11 and the weight 19
) is such that during clockwise rotation (corresponding to the state in which the pulley 5 is in contact), the pulley 5 in contact with the This creates a tendency to bite into that position more and more strongly.

Therefore, in the case of a washing machine with two extraction speeds, it is possible to use a shoe with a higher and more effective thick edge torque (curve G) at higher drum speeds. be.

Fig. 12 shows a graph showing the relationship between time t and rotational speed ■ related to the spin-drying operation and the final twist loosening operation in a washing machine equipped with the transmission shown in Figs. 7 to 10. .

Section T shows the discharge of water in the tank, at which time the drum rotates alternately in one direction and in the opposite direction.

Section U is a section for intermediate speed dehydration (for example, 450r
l"').

When the drum, and therefore the motor, is rotating slowly counterclockwise, the 16-pole winding of the motor is de-energized and the 2-pole winding is energized in a direction that causes the motor to rotate in the same counter-clockwise direction.

As mentioned above, the dehydration rotation speed is 2950X (D4/D
8) Only rpm.

Section ■ indicates the untwisting operation after dehydration at 450 rl"'.

This section is started by electrical control and continues with alternating forward and reverse rotations at 59 rpl.

Section X represents the final dewatering operation at high speed. When the motor is rotating clockwise, its 16-pole winding is de-energized and its 2-pole winding is energized to rotate the motor clockwise.

Therefore, the rotation speed during dehydration is the same as in the first embodiment, and 2950X(D5/D9)=850rp11
be equivalent to.

Section Y represents the final loosening period. This section begins with electric braking and ends with alternating forward and reverse rotation at 59 rpm.

The results achieved by the present invention are particularly useful.

Particularly noteworthy is its simple structure.

The structure of this transmission was simplified because the same part performed both engagement and disengagement with the pulley.

The transmission of the present invention is also compact, with the entire mechanism contained within a single sealed housing.

Further, in this transmission, quiet and effective braking can be applied by means of a shoe whose surface that is pressed against the cylindrical portion of the pulley is provided with a material having properties suitable for the braking function.

Furthermore, the pulley 5 fixed to the housing can withstand the maximum braking force, and the housing, which functions as a brake drum, is directly cooled by the surrounding air, so it can brake efficiently without overheating. be able to.

Finally, because the time to switch to high speed is set at a point after the drum speed has passed its critical speed, it can pass through its critical level at the highest acceleration torque, that is, in the shortest possible time.

[Brief explanation of drawings]

1 and 2 are an overall front view and a side view of an electric washing machine having a horizontal drum, and FIG. 3 is a cross-sectional view of the transmission of the present invention.
4 is a longitudinal cross-sectional view of the transmission shown in FIG. 3; FIG. 5 is a graph showing the curve of torque as a function of motor speed; and FIG.
Figure 7.8 is a graph showing the relationship between motor speed and time for a cycle carried out by a washing machine during the final spin stage.
, 9-10 are cross-sectional views and plan views showing another embodiment of the transmission of the present invention; FIG. 11 is a graph showing the torque curve as a function of motor speed of the transmission shown in FIGS. 7-10;
FIG. 12 is a graph showing the relationship between motor speed and time associated with the spin-drying operation and final untwisting operation of a washing machine equipped with the transmission shown in FIGS. 7-10. 1...Transmission, 2...2-speed motor, 4
,5,8゜9...-j'-IJ, 10...Curved driving member, 11...Curved shoe, 12,20,24...Curved spring, 19...Curved weight, 25.26 ... Spigot, 27... Opening.

Claims (1)

[Scope of Claims] 1. An inner pulley 4 and an outer pulley 5 connected by belts to pulleys 8 and 9 attached to a driven shaft, respectively, and a driving member 10 that holds a rotating shoe between the pulleys 4 and 5. , the diameter ratio of the pair of pulleys is different, the rotating shoe is elastically pushed back toward the inner pulley 4 by a spring 12, and the transmission is mounted on the shaft of the two-speed motor 2. The radially rotating shoes 11 and their return springs 12, the radially rotating weight 19 for each shoe 11, and the two pulleys 4.5 move around the axis on which they rotate. Fixing member 10 that can
and the traction force exerted by the inherent weight of the shoes 11 and their return springs when operating independently of the other parts of said transmission and under the action of centrifugal force. The shoe remains pressed against the inner pulley 4 regardless of the speed of the motor 2 when the motor 2 is running, and the weight 19 has a return spring 20 and two spigots 25, 26; 25 is engaged between the inner and outer edges of the associated shoe and is movable in the space between those edges, exerted by the inherent weight of the weight 19 and its return spring 20. Traction force is defined as the traction force that occurs when the rotational speed of the motor 2 is below a predetermined value when operating under the action of centrifugal force in cooperation with the associated shoes but independently of other parts of said transmission. By bringing the spigot 25 into contact with the inner edge of the shoe 11, the weight 19 presses the shoe 11 against the inner pulley 4, and when the rotational speed of the motor 2 is higher than the predetermined value, the spigot is brought into contact with the outer edge of the shoe. The fixing portion is configured to press the shoe 11 against the outer pulley 5 by pressing the shoe 11 against the outer pulley 5.
6 to prevent the weights 19 from reaching the end of their outward radial movement, leaving said weights 19 free in the radial direction when the motor is rotating in the opposite direction. A transmission for an electric washing machine motor, which is characterized by being able to move. 2. In the transmission according to claim 1, the fixed member 21 has an opening 27 for each weight 19, and this opening 27 is vertically divided into two regions, and the width of one region is is a transmission that is radially wider than the width of the other area. 3 The transmission according to claim 1 has two friction pieces 22 and 23, and these friction pieces are attached to the fixed member 2.
1 and keeping their friction pieces pressed against the outer pulley 5. 4. An electric washing machine having a two-speed motor that can rotate in two different directions, the washing drum of which is driven by the transmission according to any one of claims 1 to 3,
This transmission provides two operating speeds for washing and gentle spin when the motor rotates in one direction, and when the motor rotates in the second direction.
An electric washing machine characterized in that the electric washing machine is driven by the motor so as to perform high-speed rotation for powerful dehydration when rotating in the direction of the electric washing machine.