JP2000288290A - Fully automatic washing machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the durability of the rotation control mechanism of a fully automatic washing machine and to improve the ease of assembly. SOLUTION: The fully automatic washing machine comprises a washing/ dehydrating tub 1 for washing-cum-dehydration, an agitating wing 2 rotatably arranged in the washing/dehydration tub 1 to be driven to rotate by a motor, a first transmission system A to transmit the motive force of the motor to the agitating wing 2, a second transmission system B to transmit the motive force of the motor to the washing/dehydration tub 1, and a switching means Y to cut off the second transmission system B at the time of washing and to connect the second transmission system B at the time of dehydration. In the fully automatic washing machine, the second transmission system B is provided with a two-way clutch 20 to lock the rotation of a second transmission shaft 8 in both normal and reverse directions at the time of washing and to free the rotation of the second transmission shaft 8 at the time of dehydration. In addition, the switching means Y is constituted of a roller clutch 40 of which rotation is freed in both normal and reverse directions at washing and is locked at the time of dehydration.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a fully automatic washing machine.

[0002]

2. Description of the Related Art As shown in FIG. 10, generally in a fully automatic washing machine, a washing and dewatering tub 1 serving as an inner tub is provided inside an outer tub (not shown) supported by a suspension. . A stirring blade 2 such as a pulsator is provided at the bottom of the washing and dewatering tub 1, and washing or rinsing is performed by rotating the stirring blade 2 forward and reverse while the washing and dewatering tub 1 is stopped. In addition, dehydration is performed by the synchronous rotation of the stirring blade 2 and the washing and dewatering tub 1.

The stirring blade 2 and the washing / dewatering tub 1 are driven to rotate by power from a motor (not shown) serving as a common driving source. The power of the motor is supplied to the drive pulley 3 via a V belt or the like.
And transmitted from the driving pulley 3 to the stirring blade 2 via the first transmission system A and to the washing / dewatering tub 1 via the second transmission system B. The first transmission system A transmits the rotational power from the driving pulley 3 to the stirring blade 2 via the first transmission shaft 5, the speed reducer 6, and the stirring blade shaft 7, and the second transmission system B
A sleeve-shaped second transmission shaft 8 disposed on the outer peripheral side of the first transmission shaft 5, a reduction gear 6,
In addition, the power is transmitted to the washing / dewatering tub 1 via a sleeve-shaped tub shaft 9 arranged on the outer peripheral side of the stirring blade shaft 7. A brake belt 11 is arranged on the outer periphery of the speed reducer 6.
When the 11 comes into contact with or separates from the outer peripheral surface of the ring gear 6c serving as a brake drum, a braking force is applied to and released from the ring gear 6c.

[0004] The speed reducer 6 is composed of, for example, a planetary gear mechanism. The planetary gear mechanism includes a sun gear 6a, a plurality of planet gears 6b that rotate and revolve around the outer periphery of the sun gear 6a, and a planet gear 6b.
In the illustrated example, the sun gear 6a is provided on the first transmission shaft 5, and each planetary gear 6b is provided with:
The ring gear 6c is connected to the second transmission shaft 8 and the tank shaft 9, respectively, via a carrier 6d that rotatably supports this. The tank shaft 9 and the second transmission shaft 8 are mounted on a frame 12 fixedly supported on the outer tank by the upper and lower radial bearings 1.
It is rotatably supported via 3 and 14 (in the illustrated example, deep groove ball bearings).

[0005] The second transmission system B is disconnected and connected by the switching means Y. In the illustrated example, as the switching means Y,
A spring clutch 16 mounted over the lower end of the second transmission shaft 8 and both outer peripheral portions of the sleeve 5a that rotates integrally with the first transmission shaft 5 is illustrated. A one-way clutch 15 is interposed between the second transmission shaft 8 and the clutch housing 17 as clutch means X, and the one-way clutch 15 rotates the second transmission shaft 8 and the tank shaft 9 in the forward direction (in the dewatering direction). Rotation)
Are allowed, while these reverse rotations are restricted.

The rotation control of the washing and dewatering tub 1 is performed in the following procedure. At the time of washing, turn off the spring clutch 16,
That is, the diameter of the spring 16a of the spring clutch 16 is increased, the interference with the sleeve 5a integrated with the first transmission shaft 5 is released, and the second transmission shaft 8 is made free to rotate with respect to the first transmission shaft 5 (the (Second transmission system B cutoff). At the same time, the brake belt 11 is pressed against the ring gear 6c, and the rotation in the forward direction is regulated by the braking force, and the rotation in the reverse direction is regulated by the one-way clutch 15, respectively. As described above, while the second transmission shaft 8 and the tank shaft 9 are restrained in both the forward and reverse directions, only the stirring blade shaft 7 is intermittently rotated in the forward and reverse directions via the first transmission system A. The rotation of the washing and dewatering tub 1 is restricted during the washing because the washing and dewatering tub 1 is
This is because the relative rotation between the object and the laundry decreases when the rotation is performed, and the detergency decreases.

On the other hand, during dehydration, the spring clutch 16
ON, that is, the spring 16 of the spring clutch 16
The diameter of “a” is reduced, and the rotation torque is transmitted from the first transmission shaft 5 to the second transmission shaft 8 while being tight with respect to both the second transmission shaft 8 and the sleeve 5a (connection of the second transmission system B). At the same time, the brake belt 11 is separated from the ring gear 6c, the second transmission shaft 8 is rotated in the free direction (forward rotation direction) of the one-way clutch 15, and the washing and dewatering tub 1 is rotated synchronously with the stirring blade 2.
When the spin-drying is completed, the spring clutch 16 is turned off, and the brake belt 11 is brought into contact with the ring gear 6c to stop the rotation of the spin-drying tub 1.

[0008]

As described above, the rotation control of the washing and dewatering layer requires both the forward and reverse bidirectional rotation locking function and the rotation free function at the same time. This requirement was satisfied by using both. However, due to prolonged use,
Deterioration of the brake belt, wear of the brake drum, and the like occur, and the reliability of the lock function by the brake belt is not always high.

Further, as other items to be improved,
There is some difficulty in assembling the spring clutch 16, which leads to an increase in assembly cost. Next, when the tank shaft 9 rotates (during dehydration), the spring 16 a of the spring clutch 16 is attached to the outer peripheral surface of the second transmission shaft 8. Due to frictional contact, there is a concern that torque loss and wear of the second transmission shaft 8 may occur.

Accordingly, an object of the present invention is to solve the above problems and improve the durability, assemblability, and torque characteristics of a fully automatic washing machine.

[0011]

According to the present invention, there is provided a washing and dewatering tub for performing both washing and spinning, and a rotatably disposed in the washing and dewatering tub, which is rotatably driven by the power of a drive source. Agitating blades, a first transmission system for transmitting the power of the drive source to the agitating blades, a second transmission system for transmitting the power of the drive source to the washing and dewatering tub, and shutting off the second transmission system during washing. In a fully automatic washing machine having a switching means for connecting a second transmission system during dehydration, the switching means is constituted by a roller clutch which is free to rotate in both forward and reverse directions during washing, and is rotationally locked during dehydration.

The above-mentioned roller clutch is a one-way clutch having two modes, a forward and reverse bidirectional rotation free mode and a rotation lock mode. At the time of washing, the roller clutch is set to the washing mode, that is, free to rotate in both the forward and reverse directions. For example, the washing and dewatering tub is restrained by the clutch means X and the brake belt to stop the rotation, and only the stirring blade is passed through the first transmission system. Is rotated forward and backward. At the time of spin-drying, the roller clutch is set in spin-drying mode, that is, in a rotation lock (at least rotation lock in the spin-drying direction). Perform dehydration.

According to the present invention, a washing and dewatering tub for washing and dewatering, a stirring blade rotatably disposed in the washing and dewatering tub and driven to rotate by the power of a driving source, and a stirring blade for rotating the power of the driving source are provided. Transmission system for transmitting the power of the drive source to the washing and dewatering tub, and disconnecting the second transmission system during washing and connecting the second transmission system during dehydration. In a fully automatic washing machine having switching means, the second transmission system locks rotation in both forward and reverse directions during washing,
A two-way clutch that is free to rotate during dehydration is provided, and the switching means is a roller clutch that is free to rotate in both forward and reverse directions during washing, and is rotation locked during dehydration.

The two-way clutch has two modes (a washing mode and a spin-dry mode): a forward / reverse bidirectional rotation lock of the spin-drying tub and a spin-free (idling) mode. Also,
The roller clutch as the switching means is a one-way clutch having two modes, a washing mode in which the rotation is free in both forward and reverse directions and a spin-drying mode in which the rotation is locked. During washing, both the roller clutch and the two-way clutch are switched to the washing mode, and the roller clutch is free to rotate in both the forward and reverse directions.
The transmission system is shut off, and the forward / reverse rotation lock of the two-way clutch restrains the rotation of the washing and dewatering tub in both the forward and reverse directions, thereby preventing the washing and dewatering tub from rotating. On the other hand, at the time of spin-drying, the roller clutch and the two-way clutch are switched to the spin-drying mode. Rotate the aquarium. In this case, both the rotation locking direction of the roller clutch and the rotation free direction of the two-way clutch match the rotation direction at the time of spin-drying. The free rotation of the two-way clutch may be either free rotation in both forward and reverse directions or free rotation only in the forward direction (dehydration direction).

The two-way clutch has a plurality of clutch grooves on an inner peripheral surface, and an outer ring that forms a wedge space symmetrical in both forward and reverse directions with a rotating shaft to be controlled at each clutch groove portion. A plurality of rollers which can be engaged and disengaged from the wedge space, a resin cage provided with a pocket for accommodating the rollers, and which is swingably disposed on the inner diameter portion of the outer ring, and a swing of the cage. And a drag projection that is provided on the inner diameter portion of the retainer and that comes into contact with the outer periphery of the rotating shaft with interference.
The drag projection may be formed integrally with the inner diameter portion of the retainer, or may be formed by providing a drag member such as a separate drag strip on the inner diameter portion.

The drag projection is in contact with the outer peripheral surface of the rotating shaft with a tight allowance. When the rotating shaft rotates, the cage receives the frictional force generated at the contact portion between the drag projection and the rotating shaft, and the retainer is driven by the rotating shaft. And rock. The swing range of the retainer is limited by the first stopper means. When the retainer swings, the rollers housed in the pockets of the retainer are pushed into the wedge space on the swing side, and the rotation of the rotation shaft is locked by engaging with the wedge space. When the rotating shaft rotates in the opposite direction in this state, the retainer swings in the opposite direction due to the frictional force of the drag projection, and the rollers engage with the wedge space in this direction to lock the rotation of the rotating shaft. . That is, the rotation shaft is automatically locked in either the forward or reverse rotation direction by the action of the drag projection. If the position of the retainer is fixed by the first stopper means in a state where the rotation of the rotary shaft is locked, the movement of the rollers to the wedge space in the opposite direction is regulated by the retainer, so that the rotation of the rotary shaft in the opposite direction is performed. Becomes free. On the other hand, when the retainer is held at the neutral position where the rollers do not contact the outer ring by the first stopper means, the rotation of the rotating shaft in both the forward and reverse directions can be made free. If the swing of the cage is controlled by the first stopper means in this way, it is possible to select any one of forward rotation free, reverse rotation free, and both forward and reverse rotation free of the rotating shaft.

The roller clutch has a plurality of clutch grooves on an inner peripheral surface, and each of the clutch grooves includes an outer ring that forms a one-way wedge space with a rotation shaft to be controlled, and a wedge space. A plurality of rollers arranged so as to be able to engage and disengage with each other, a resin retainer provided with a pocket for accommodating the rollers and slidably disposed on the inner diameter portion of the outer ring, and a resin retainer for controlling the rotation of the retainer. And second stopper means.

For example, when the outer ring is rotated in the direction opposite to the direction in which the wedge space is formed, the rollers accommodated in the pockets of the retainer engage with the wedge space, so that the outer ring and the rotation shaft are locked,
Torque is transmitted from the outer ring to the rotating shaft (connection of the second transmission system). In this case, if the locking direction is made to coincide with the spin-drying direction, the spin-drying tub can be rotated to spin-dry. On the other hand, during the washing, if the retainer is swung in the direction opposite to the direction of the wedge space by the second stopper means, the rollers are pushed in the direction by the retainer, so that the rollers are separated from the wedge space and the clutch is disengaged. Non-contact with the groove. In this case, no matter which direction the outer ring is rotated, the rollers do not engage with the wedge space, and the space between the outer ring and the rotation shaft is free in the forward and reverse rotation directions (interruption of the second transmission system).

The two-way clutch is disposed between a fixed member and a rotating member constituting a second transmission system. For example, the two-way clutch is configured by connecting an outer ring to the fixed member and using the rotating member as the rotating shaft. , Are incorporated in the second transmission system. On the other hand, the roller clutch is disposed between the two rotating members constituting the second power transmission system, and connects one of the rotating members to the outer ring and uses the other rotating member as the above-mentioned rotating shaft, thereby achieving the second rotation. Installed in the transmission system. In this case, in addition to the outer ring being the input side and the rotating shaft being the output side, the rotating shaft may be the input side and the outer ring may be the output side.

If a flange portion is integrally provided on the outer ring of the two-way clutch and the flange portion is fixed to a fixing member such as a frame, a member (such as the clutch housing 17) for fixing the two-way clutch to the fixing member is unnecessary. Thus, the number of parts can be reduced, the diameter of the clutch can be reduced, and the like.

In order to simplify the structure, to reduce the weight, and to reduce the size, a bearing for rotatably supporting the washing and dewatering tub may be provided integrally with the two-way clutch.

The stopper means of the two-way clutch can be driven by a solenoid.

When the above-described two-way clutch is used, the two-way clutch is held in a rotation-free state when the power supply to the drive source is cut off, so that a sudden stop of the washing and dewatering tub when the power supply is cut off is prevented. desirable.

When the roller clutch has a radial bearing integrally, the clutch portion is not misaligned, and the clutch function is stabilized.

[0025]

Embodiments of the present invention will be described below.

FIG. 1 shows a rotary drive unit of a fully automatic washing machine according to the present invention. This fully automatic washing machine differs from the conventional one shown in FIG. 10 in that a two-way clutch 20 shown in FIGS. 2 to 5 is used in place of the one-way clutch 15 as the clutch means X, and a switching means Y is used. The roller clutch 40 shown in FIGS. 6 to 9 is used in place of the spring clutch 16 of FIG. Other substantial structures
Same as 10. That is, the power of the motor as a driving source is supplied from the driving pulley 3 to the stirring blade 2 via the first transmission system A including the first transmission shaft 5, the speed reducer 6, and the stirring blade shaft 7.
, And similarly transmitted from the driving pulley 3 to the washing and dewatering tub 1 via a second transmission system B including a second transmission shaft 8, a reduction gear 6, and a tub shaft 9.

As shown in FIG. 2, the two-way clutch 20
The outer ring 21, a resin cage 22 swingably inserted into the inner diameter of the outer ring 21, rollers 23 (for example, needle rollers) housed in pockets 22 a of the holder 22, A first stopper means 28 composed of a drag projection 24 formed integrally, a stopper pin 25 fixed to one end face of the retainer 22 and a stopper groove 26 formed on one end face of the outer ring 21 is mainly used. Components. The retainer 22 is axially restrained by a stepped portion 21 a formed on the inner diameter portion of the outer ring 21 and a retaining ring 27, and the swing range thereof is limited by the engagement between the stopper pin 25 and the stopper groove 26. As shown in FIG. 4B, the drag projection 24 of the present embodiment has a lip shape and projects in a direction shifted in the circumferential direction with respect to the radius line. Then, the two drag projections 24 shifted in opposite directions in the circumferential direction.
And a plurality of pairs are formed on the inner diameter portion on one end face side of the retainer 22 at equal circumferential intervals. In addition, by using a shell type press-formed steel plate as the outer race 21, cost reduction, weight reduction, and mass production can be achieved. The drag projection 24 may be formed in a rib shape formed over the entire circumference in the circumferential direction or partially, or by providing a drag member such as a separate drag strip.

As shown in FIG. 3, the two-way clutch 20
The rotary shaft R is inserted into the inner diameter side of the roller 23 for use. A plurality of clutch grooves 27 are formed on the inner peripheral surface of the outer ring 21 at equal circumferential intervals. Is formed.
The rollers 23 are arranged in this wedge space so as to be engageable and disengageable.
The two pockets 22a are resiliently pressed from both sides by spring members 28 disposed on both side walls of the pocket 22a. The spring member 28 plays a role of quickly shifting the rollers 23 from the disengaged state to the engaged state, and increasing the responsiveness of the clutch.

The rollers 23 are arranged in the same number as the clutch grooves 27, and the pockets 22a of the retainer 22 are formed in the same number as the rollers 23. The tip of the drag projection 24 is elastically in contact with the outer peripheral surface of the rotating shaft R with an interference, and the interference can be adjusted by the length of the protrusion of the drag projection 24 and the like. The stopper pin 25 may be formed integrally with the retainer 22 (see FIG. 5).

The two-way clutch 20 is formed, for example, by fitting the outer ring 21 to the inner peripheral portion of the clutch housing 17 and inserting the second transmission shaft 8 as the rotation shaft R into the inner diameter side of the roller 23, for example. It is incorporated into the second transmission system B.

As shown in FIG. 3, for example, when the second transmission shaft 8 rotates clockwise, the friction generated at the contact portion between the drag projection 24 and the second transmission shaft 8 that comes into contact with the second transmission shaft 8 with interference. The retainer 22 swings clockwise by the force. Then, the roller 23 is pressed by the retainer 22 and engages with the clockwise wedge space, whereby the rotation of the second transmission shaft 8 is locked. When the second transmission shaft 8 rotates counterclockwise from this state, the cage
The rotation of the second transmission shaft 8 is locked when the roller 22 swings counterclockwise and the roller 23 engages with the counterclockwise wedge space. That is, this clutch does not require any operation, and can automatically lock the forward / reverse rotation of the second transmission shaft 8.

Next, in the state shown in FIG.
The swing of the retainer 22 is restricted by engaging the stopper groove 25 with the clockwise side wall of the stopper groove 26. However, if the stopper pin 25 is fixed in this state, the counterclockwise movement of the second transmission shaft 8 will occur. The rotation in the direction can be made free. Conversely, if the stopper pin 25 is fixed while being engaged with the counterclockwise side wall of the stopper groove 26, the clockwise rotation of the second transmission shaft 8 can be made free. Furthermore, if the stopper pin 25 is fixed in the neutral position and the rollers 23 are not in contact with the outer ring 21, the clockwise and counterclockwise rotation of the second transmission shaft 8 can be made free.

The switching of the two-way clutch 20 can be performed by a mode switching mechanism for turning on / off an external force applied to the retainer 22, and the switching is performed by, for example, swinging of a switching lever 31 shown in FIG. In this case, in the washing mode, the switching lever 31 is separated from the stopper pin 25 as shown in FIG. 7A, and in the spin-drying mode, the switching lever 31 is pressed against the stopper pin 25 as shown in FIG. An external force F is applied to fix the retainer 22 at the rotation free position. As means for swinging the switching lever 31, a solenoid (not shown) or the like can be considered. The solenoid converts electromagnetic energy into mechanical movement by energizing the exciting coil and moving a movable member such as an iron core, so that the above-mentioned switching operation can be fully automated at low cost and easily. Is high. In this case, as shown, in the washing mode (FIG. 7A), the switching lever 31 is pressed and fixed to the retracted position by a solenoid against the elastic force of the elastic member 32 such as a torsion coil spring. It is preferable that the pressing force of the solenoid is released and the external force F is applied to the retainer 22 by the resilience of the elastic member 32.
With this structure, the retainer 22 is fixed to the rotation free position shown in FIG. 3B by the elastic force of the elastic member 32 even when the power supply is suddenly stopped due to a power failure or an outlet being disconnected during dehydration. Therefore, the washing and dewatering tub 1 can be naturally stopped while rotating by inertia. Conversely, if the rotation of the retainer 22 is locked in both forward and reverse directions when the power supply is stopped (the state shown in FIG. 7A), the washing / dewatering tub 1 stops suddenly, and the impact becomes excessive. The position (or posture) of the switching lever 31 in the washing mode (FIG. 7A) and the dehydration mode (FIG. 9B) is determined by the positioning member 33.

As shown in FIGS. 6 and 7, the roller clutch 40 as the switching means Y includes an outer ring 41 and a resin cage 4 which is inserted into the inner diameter of the outer ring 41 so as to be swingable in the circumferential direction.
2. Rollers 43 (for example, needle rollers) housed in pockets 42a of the retainer 42 and a second stopper means 44 for controlling the swing of the retainer 42 are main components. As shown in FIG. 8, the roller clutch 40 is used by inserting a rotating shaft R into the inner diameter side of a roller 43. A plurality of clutch grooves 47 are formed on the inner peripheral surface of the outer ring 41 at equal circumferential intervals, and a wedge space is formed between each clutch groove 47 and the outer peripheral surface of the rotating shaft R in the counterclockwise direction in FIG. Is formed. The rollers 43 are arranged as many as the clutch grooves 47, and the pockets 42a of the retainer 42 are formed as many as the rollers 43. The roller 43 is disposed so as to be able to engage and disengage from the wedge space, and is resiliently pressed by a spring member 48 disposed on the clockwise rotation side wall of the pocket 42a of the retainer 42.

In FIG. 8, for example, when the outer ring 41 rotates clockwise, the rollers 43 engage with the wedge space, so that the outer ring 41 rotates.
And the rotating shaft R are locked, and torque is transmitted from the outer race 41 to the rotating shaft R (dehydration mode). In contrast, the outer ring
When 41 rotates in the counterclockwise direction, the outer ring 41 is free to rotate because the rollers 43 separate from the wedge space. Meanwhile, cage
When 42 is fixed at the position slightly swung clockwise, the rollers
Since the movement range of 43 is displaced in the clockwise direction, the rollers 43 are separated from the wedge space and reach the neutral position, and do not contact the clutch groove 47. In this case, the roller 43 does not engage with the wedge space regardless of the direction in which the outer ring 41 is rotated. Therefore, the space between the outer ring 41 and the rotation axis R is free in the forward and reverse rotation directions. Transmission of torque to the rotating shaft R is interrupted (washing mode).

As shown in FIGS. 7 (a) and 7 (b), one end of the outer race 41 has a flange 41a bent to the inner diameter side, and the flange 41a.
A cutout portion 41b is formed at a plurality of positions (for example, three positions) at equal circumferential positions. At one end of the retainer 42, a plurality (for example, three) of claw portions 42b protruding in the axial direction are formed at circumferentially equal positions, and at the other end, an annular flange portion 42c extending to the outer diameter side is formed. ing. The claw portion 42b is an outer ring
It is adapted to be engageable with the 41 notch 41b. Claw part 42b
Is smaller by a predetermined amount than the circumferential dimension of the notch portion 41b, so that the retainer 42 can swing in the circumferential direction with respect to the outer ring 41 by this dimensional difference. From the relationship, a second stopper means 44 for controlling the swing of the retainer 42 is configured. A spline-shaped engaging portion 42d is provided on the outer peripheral portion of the flange portion 42c. As shown in FIG. 6, on the side of the flange portion 42c of the roller clutch 40,
The switching lever 51 is arranged to be able to move forward and backward. The end of the switching lever 51 is normally engaged with the engaging portion 42d of the retainer 42.
To fix the position of the retainer 42 to the free rotation position, and to retract and open the retainer 42 during dehydration. The switching lever 51 can be driven in conjunction with the switching lever 31 of the two-way clutch 20.

In the roller clutch 40, for example, the outer ring 41 is fitted and fixed to the inner periphery of a cylindrical clutch housing 52 having a U-shaped cross section, and the second transmission shaft 8, for example, is inserted as the rotation axis R into the inner diameter side of the roller 43. Thereby, it is incorporated in the second transmission system B. The clutch housing 52 is connected to the first transmission shaft 5 and rotates forward and backward integrally therewith. 53 is a sliding bush, which is attached to the lower end of the second transmission shaft 8 and
And the rotation of the clutch housing 52 is supported.

In the above configuration, the rotation control of the tub shaft 9 and the stirring blade shaft 7 at the time of washing, dehydrating, and stopping can be performed, for example, in the following procedure.

At the time of washing, the two-way clutch 20 and the roller clutch 40 are switched to the washing mode. That is, the roller clutch 40 is free to rotate forward and reverse (the switching lever 51 is
To make the outer race 41 and the second transmission shaft 8 free to rotate) to shut off the second transmission system B and to lock the two-way clutch 20 in the forward and reverse bidirectional rotation. In this case, the rotation of the second transmission shaft 8 is locked in both forward and reverse directions by the two-way clutch 20, and only the first transmission shaft 5 rotates forward and reverse. 1 can be stopped.

At the time of spin-drying, the two-way clutch 20 and the roller clutch 40 are switched to the washing mode. That is, by rotating the roller clutch 40 (by releasing the switching lever 51 from the engaging portion 42d of the retainer 42 and releasing the control of the retainer 42,
The outer ring 41 and the second transmission shaft 8 are locked), the second transmission system B is connected, and the two-way clutch 20 is free to rotate forward (the “forward rotation” direction matches the rotation direction during dehydration). To Since the second transmission shaft 8 is free to rotate forward,
The washing and dewatering tub 1 is rotatably driven in a dehydrating direction via a second transmission system B, and is driven by a stirring blade 2 which is driven via a first transmission system A.
And rotate synchronously. When dehydration is completed, the two-way clutch 20
The rotation drive source is stopped in a state where is kept in the dehydration mode (free of normal rotation), and the rotation of the tank shaft 9 is stopped by sliding the brake belt 11 on the outer peripheral surface of the ring gear 6c. In this example, the two-way clutch 20 is used at the time of dehydration and after the completion of dehydration.
Are free to rotate in the normal direction, but the stopper pin 25 may be fixed to the neutral position to make the rotation free in both the forward and reverse directions. Alternatively, a braking function may be provided from a motor side by providing a braking function to a motor (not shown) serving as a driving source. In this case, the brake belt 11 can be omitted.

As described above, according to the present invention, unlike the conventional brake belt, the rotation of the tub shaft 9 is not stopped at the time of washing, and only the rotation stop or the emergency stop after the completion of dehydration is performed. Do. Therefore, deterioration of the brake belt 11 and wear of the brake drum due to long-term use hardly occur, and the durability of the fully automatic washing machine can be improved.

Further, since the roller clutch 40 is used instead of the spring clutch 16 (see FIG. 5) in the conventional configuration, the assembling property is excellent. That is, the roller clutch 40 is set in the clutch housing 52 in advance,
In this state, it can be inserted into the outer peripheral side of the second transmission shaft 8 together with the clutch housing 52, so that assembly is easy. Also, at the time of washing (when the rotation of the roller clutch 40 is free), the rollers 43 of the roller clutch 40
47 or the outer peripheral surface of the second transmission shaft 8
No worry about torque loss or wear.

FIG. 5 shows another embodiment of the two-way clutch. The two-way clutch 20 'is provided with a flange portion 21b' on an outer race 21 ', and the flange portion 21b'
The structure is fixed to a fixing member such as the above. Compared with the structure of FIG. 2, the clutch housing 17 is not required, so that the cost can be reduced by reducing the number of parts and the diameter of the clutch mounting portion can be reduced. Also, in the clutch 20 'of FIG.
A radial bearing that rotatably supports the washing and dewatering tub 1 (FIG. 1)
13 and 14), bearing 14 adjacent to clutch means X
Is integrated with the two-way clutch 20 'so that the clutch alone can support the radial load. That is, the roller 2 is attached to the inner diameter of the outer race 21 'of the two-way clutch 20'.
3 ', a resin-made retainer 22', a clutch assembly including a spring (not shown) and the like are incorporated, and the radial bearing 14 is housed therein, as compared with the structure used together with the radial bearing 14 (see FIG. 1). Simplification of the structure, compactness, and weight reduction are achieved. Cage 22 'is stopper pin 2
5 'and integrally formed with radial bearing 14 and retaining ring 27'
Or by the step 21a 'and the retaining ring 27' from both sides in the axial direction. As the radial bearing 14, besides the oil-impregnated sliding bearing shown in FIG. 5, a rolling bearing using a ball or a roller as shown in FIG. 1 can be used as the rolling element 14a. When a rolling bearing is used, the bearing outer ring 14b can be shared with the outer ring 21 of the clutch, and the inner ring 14c is omitted, and the inner raceway surface is directly connected to the outer peripheral surface of the rotary shaft (second transmission shaft 8). It can also be formed. In the illustrated example, the outer ring 21 'is provided with the flange portion 21b' and the radial bearing 14 is integrated with the two-way clutch 20 ', but only one of the structures may be employed.

In the embodiment shown in FIG. 9, a clutch part and a radial bearing 54 are used as switching means Y for switching between washing and dehydration.
And a roller clutch 40 in which the above is combined. This is to stabilize the clutch function by adopting a structure in which misalignment is not applied to the clutch portion. Roller 43, retainer 42, spring member
48, and a pair of radial bearings 54 arranged on both sides of the retainer 42 are accommodated, and are prevented from coming off on both sides in the axial direction by flanges 41b and 41c bent from both sides of the outer ring 41 to the inside diameter side. You. As the radial bearing 54,
In addition to the oil-containing sliding bearing, a rolling bearing using a ball or a roller as a rolling element can also be used. This embodiment is
6 to 8, the rotation axis R is set on the input side,
The outer ring 41 is on the output side. Specifically, the outer ring 41 is fitted and fixed to the inner peripheral portion of the second transmission shaft 8, and the first transmission shaft 5 is inserted into the inner peripheral portion of the roller 43 as the rotation axis R. Have been. Other basic configurations and functions are the same as those of the roller clutch 40 shown in FIGS. 1 to 3, and a detailed description thereof will be omitted.

In the above description, a structure in which the power of the drive source is transmitted to the stirring blade 2 via the speed reducer 6 has been exemplified.
The present invention is not limited to this, and is also applicable to a direct drive type fully automatic washing machine that directly transmits the output of the drive source to the stirring blade 2 without the intervention of a speed reducer. Further, the structures of the stopper means 28, 44 and the switching levers 31, 51 are arbitrary,
An arbitrary structure can be adopted or can be appropriately combined as long as the structure can control the swing of the retainer 42 within a predetermined range.

[0046]

According to the present invention, automatic switching between forward and reverse bidirectional rotation of the washing and dewatering tub with respect to the washing machine frame and free rotation (both forward and reverse or forward free rotation) can be easily switched. Therefore, the rotation control of the washing and dewatering tub conventionally performed by the one-way clutch and the brake belt can be performed by the two-way clutch unit. Therefore, the brake belt is used only for stopping after the completion of spin-drying or for emergency stop, the frequency of use of the brake belt can be reduced, the durability can be improved, and the brake belt can be made unnecessary. Further, the rotation control mechanism can be simplified, its weight and size can be reduced, and the switching can be easily performed by a mode switching mechanism having a simple structure.

Further, since a roller clutch is used in place of the spring clutch in the conventional configuration, the assemblability is improved. Furthermore, when the roller clutch is free to rotate, the rollers of the roller clutch do not contact the second transmission shaft or the like. Therefore, there is no need to worry about torque loss and wear, and the torque characteristics and durability can be improved.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a fully automatic washing machine according to the present invention.

FIG. 2 is a cross-sectional view of a two-way clutch (FIG. A), an enlarged cross-sectional view as viewed from a direction b (FIG. B), and a plan view as viewed from a direction c (FIG. C).

FIG. 3 is an enlarged cross-sectional view showing a periphery of a clutch groove in FIG. 2 (b).

FIG. 4 is a schematic view showing a switching mechanism of a two-way clutch.

FIG. 5 is a sectional view showing another embodiment of the two-way clutch.

FIG. 6 is an enlarged sectional view showing a fully automatic washing machine according to the present invention.

FIG. 7 illustrates a roller clutch used in the fully automatic washing machine, wherein FIG. 7 (a) is a cross-sectional view taken along line aa,
(B) is a front view seen from the direction b.

FIG. 8 is an enlarged sectional view showing a peripheral portion of a clutch groove of the roller clutch.

FIG. 9 is a sectional view showing another embodiment of the roller clutch.

FIG. 10 is a sectional view showing a conventional fully automatic washing machine.

[Explanation of symbols]

 Reference Signs List A First transmission system B Second transmission system R Rotating shaft X Clutch means Y Switching means 1 Washing / dewatering tub 2 Stirrer blade 5 First transmission shaft 6 Reducer 7 Stirrer blade shaft 8 Second transmission shaft 9 Tank shaft 12 Fixed Member (frame) 13/14 Bearing 17 Clutch housing 20 Two-way clutch 21 Outer ring 21b Flange part 22 Cage 22a Pocket 23 Roller 24 Drag projection 25 Stopper pin 28 First stopper means 31 Switching lever 32 Elastic member 40 Roller clutch 41 Outer ring 42 Cage 43 Roller 44 Second stopper means 51 Switching lever 54 Radial bearing

Continued on front page F term (reference) 3B155 AA01 AA06 BA18 BB18 CA06 CB06 DC23 EA09 HB02 HB03 HB09 HB17 HB19 HB21 HB36 LB20 LB25 MA01 MA02

Claims (9)

[Claims] 1. A washing and dewatering tub for washing and dewatering, a stirring blade rotatably disposed in the washing and dewatering tub and rotationally driven by the power of a driving source, and a stirring blade for transmitting the power of the driving source to the stirring blade. One transmission system, a second transmission system for transmitting the power of the drive source to the washing dehydration tub, and shut off the second transmission system during washing,
In a fully automatic washing machine having switching means for connecting a second transmission system during dehydration, the switching means is constituted by a roller clutch which is free to rotate in both forward and reverse directions during washing, and is rotationally locked during dehydration. And a fully automatic washing machine. 2. A washing and dewatering tub for washing and dewatering, a stirring blade rotatably disposed in the washing and dewatering tub, and rotatably driven by the power of a driving source, and a stirring blade for transmitting the power of the driving source to the stirring blade. One transmission system, a second transmission system for transmitting the power of the drive source to the washing dehydration tub, and shut off the second transmission system during washing,
A fully automatic washing machine having switching means for connecting a second transmission system during spin-drying, wherein a two-way clutch that locks rotation in both forward and reverse directions during washing with the second transmission system and is free to rotate during spin-drying. Wherein the switching means comprises a roller clutch which is free to rotate in both the forward and reverse directions during washing, and is locked for rotation during spin-drying. 3. The two-way clutch has a plurality of clutch grooves on an inner peripheral surface, and forms a wedge space symmetrical in both forward and reverse directions between each clutch groove portion and a rotating shaft to be controlled. A resin cage having an outer ring, a plurality of rollers arranged to be engaged with and disengaged from the wedge space, a rocker disposed in the inner diameter portion of the outer ring, and having a pocket for accommodating the rollers; 3. A fully automatic apparatus according to claim 2, further comprising a first stopper means for controlling swinging, wherein a drag projection which comes into contact with an outer periphery of said rotary shaft with an interference is provided on an inner diameter portion of said retainer. Washing machine. 4. An outer ring having a plurality of clutch grooves on an inner peripheral surface thereof and forming a one-way wedge space between each clutch groove portion and a rotation shaft to be controlled, a wedge space. A plurality of rollers arranged so as to be able to engage and disengage with each other; a resin cage provided with a pocket for accommodating the rollers, which is swingably disposed on the inner diameter portion of the outer race; and controlling the swing of the cage. 3. A fully automatic washing machine according to claim 1, further comprising a second stopper means. 5. The fully automatic washing machine according to claim 3, wherein a flange portion is integrally provided on an outer ring of the two-way clutch, and the flange portion is fixed to a fixing member. 6. The fully automatic washing machine according to claim 2, wherein a bearing that rotatably supports the washing and dewatering tub is provided integrally with the two-way clutch. 7. The fully automatic washing machine according to claim 2, wherein the first stopper means of the two-way clutch is driven by a solenoid. 8. The fully automatic washing machine according to claim 2, wherein the two-way clutch is held in a rotation-free state when the power supply to the drive source is cut off. 9. The fully automatic washing machine according to claim 1, wherein said roller clutch integrally has a radial bearing.