JPH08117480A - Dewatering washing machine - Google Patents

Abstract

PURPOSE: To effectively reduce the vibration amplitude of an external tank in dewatering operation. CONSTITUTION: Suspension rods 5-8 for suspending the external tank 4 are provided with conversion levers 10-13 which face the outer periphery of the external tank 4, whose vibratory displacement is made to operate on the conversion levers 10-13; and then a pressing force in a 90 deg. phase advance angle direction is made to operate on the external tank 4, thereby obtaining vibration damping operation.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dewatering washing machine in which a vibration phenomenon occurs due to imbalance in an inner tub during dewatering operation. The vibration amplitude is reduced, and in particular, the resonance point in the imbalance resonance is reduced. The present invention relates to a dehydration washing machine that reduces resonance amplitude when passing through.

[0002]

2. Description of the Related Art A dewatering washing machine has a hollow ring-shaped balance ring filled with liquid at the upper edge of the inner tub in order to reduce the vibration amplitude of the outer tub when passing through the resonance point at the start of the dewatering operation. Further, a buffer is provided in the outer tank or the outer frame. The buffer body in this dehydration washing machine is configured such that a vibrating body that vibrates along with whirling of the outer tub is brought into contact with a suspension rod, and vibration of the vibrating body is regulated and friction is damped so that the outer tub of the outer tub when passing through a resonance point is It serves to reduce the vibration amplitude. As such an anti-vibration mechanism, as disclosed in Japanese Utility Model Laid-Open No. 62-50582, a cushioning member made of an elastic material is provided on the outer peripheral surface of the outer tub at a position facing the suspension rod at a predetermined swinging gap. Some have been installed via.

[0003]

Since the vibration isolating mechanism in the prior art as described above regulates the shake by contact,
There is a problem in that the effect is not sufficient, or the vibration is transmitted to the outer frame or the like through the cushioning body and causes vibration noise from the outer frame or movement (positional shift) of the washing machine.

An object of the present invention is to provide a dewatering washing machine in which a vibration damping force is applied to a whirling outer tub to reduce the vibration amplitude.

Another object of the present invention is to provide a dewatering washing machine which can reduce the resonance amplitude of the outer tub when passing through the resonance point (resonance speed) at the time of starting the dewatering operation.

Still another object of the present invention is to provide a dewatering washing machine which does not become large in size by installing a vibration damping mechanism which effectively reduces the vibration amplitude of the outer tub.

[0007]

The feature of the present invention is that the dewatering is provided with an inner tank having a stirring blade at the center of the bottom, an outer tank containing the inner tank, and an outer frame elastically supporting the outer tank. The washing machine is provided with a vibration damping mechanism for generating a vibration damping force having a phase advance component of 90 degrees with respect to the whirling displacement direction of the outer tub and acting on the outer tub.

Specifically, the vibration damping mechanism is provided on the outer frame side so as to face the outer periphery of the outer tub, and rotates in response to the sway of the outer tub to rotate 90 degrees with respect to the swaying direction. Is provided with a direction changing member that generates a vibration damping force that presses the outer tub in the direction of the phase advance angle, or a member on the outer frame side that is provided on the outer periphery of the outer tub and moves with the swing of the outer tub. The outer tank is provided with a direction changing member that generates a vibration damping force in the direction of the phase advance angle of 90 degrees with respect to the shake direction.

Further, it is characterized in that the vibration damping mechanism is installed by utilizing the spaces at the four corners in the outer frame.

[0010]

Operation: The vibration (whirling) of the outer tub of the dehydration washing machine is considered as a circular motion, and X and Y which are orthogonal to the horizontal cross section of this outer tub.
Taking the axis as an axis and the displacements in the respective directions as x and y, x = a · cosωt y = a · sinωt. At this time, the time differential terms dx / dt and dy / dt of x and y are as follows: dx / dt = −aω · sin ωt = −ω · y dy / dt = aω · cosωt = ω · x. The damping force in the x and y directions is dx, respectively.
Since it is a force proportional to / dt and dy / dt, from the above formula, the damping force in the x direction is proportional to the displacement in the -y direction. The damping force in the y direction is replaced with the force proportional to the displacement in the x direction. It is possible. That is, the damping force in each direction is
This means that the force is in a direction 90 degrees ahead of the displacement direction. The damping mechanism according to the present invention generates such a damping force and causes it to act on the outer tank.

The direction changing member provided on the outer frame side which is the stationary side with respect to the outer tank rotates in response to the shake (displacement) of the outer tank,
A force in a phase that is 90 degrees ahead of the displacement direction is applied to the outer tank. This force acts on this outer tank as a vibration damping force to reduce the vibration amplitude of the outer tank.

Further, when the outer tank is displaced, the direction changing member moves in a substantially horizontal cross section and abuts against a member on the outer frame side to restrain the movement of the outer tank. A force in a phase advance of the displacement direction acts on the outer tub, and the component whose phase advances by 90 degrees acts on the outer tub as a vibration damping force to reduce the vibration amplitude of the outer tub.

Further, the damping mechanism constituted by utilizing the spaces at the four corners in the outer frame suppresses the enlargement of the machine body.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS. FIG. 1 is a partially developed vertical sectional side view of a dewatering washing machine according to the present invention, and FIG. 2 is an AA cross-sectional plan view thereof.

This dewatering washing machine has an inner tub 3 having a hollow ring-shaped balance ring 1 in which a liquid is sealed at its upper edge, a stirring blade 2 at the bottom, and an outer tub 4 containing the inner tub 3. An outer frame 9 that elastically supports the outer tub 4 in the space portions at the four corners by the suspension rods 5 to 8, and an outer frame 9 that is freely movable in a specific direction and rotatably installed in the middle of the suspension rods 5 to 8. Outer frame 9
It is provided with L-shaped conversion levers 10 to 13 which are direction conversion members located in the spaces of the four corners.

The stirring blade 2 is independently driven to rotate by a motor 14 via a pulley / belt system 15 and a clutch 16 at the time of washing, and together with the inner tub 3 at the time of dehydration.

The motor 14 and the clutch 16 are fixed to the center base 17 with bolts, and the center base 17 is fixed to the bottom surface of the outer tank 4 with bolts. The inner tank 3 is supported by the output shaft of the clutch 16 via a flange 18.

1 and 2 show only the vibration control mechanism which is the main element of the dehydration washing machine according to the present invention and the basic constituent elements of the washing machine, and other elements such as a panel switch are omitted. are doing.

Both ends of the L-shaped conversion levers 10 to 13, which are the main constituent elements of the vibration damping mechanism, are 1 / l of the outer circumference of the outer tank 4.
Engagement holes 10a to 10a, which have a length facing each other at a position separated by four arcs (90 degrees) and are formed in the bent portion at the intermediate position
13a engages with the suspension rods 5 to 8 and is supported so as to be movable and rotatable on a horizontal plane. The hanging rods 5 to 8 are stoppers 5 for restraining the vertical movement of the conversion levers 10 to 13.
a, 5b.

Engagement holes 10a of the conversion levers 10-13
Each of the conversion levers 13a is formed in a rectangular shape so that the conversion levers 10 to 13 can freely move in a horizontal direction in a certain direction and are rotatably engaged with the hanging rods 5 to 8.
The direction of the long sides of the engagement holes 10a to 13a that allow the horizontal movement of the conversion levers 10 to 13 is determined from the rotation direction of the inner tank 3, and as shown in the figure, changes from the X axis to the Y axis. If the rotation direction (clockwise direction) is taken, the conversion lever 1
The engaging holes 10a and 12a of 0 and 12 are
0 and 12 move freely in response to the vibration force in the Y-axis direction, and are restrained by the suspension rods 5 and 7 to rotate in response to the vibration force in the X-axis direction. It is formed so as to be parallel to the Y axis, and the engaging holes 11a of the conversion levers 11 and 13 are
The long side of Xa has an X-axis so that it can rotate while being restrained by the suspension rods 6 and 8 with respect to the vibration force in the Y-axis direction and freely follow the vibration force in the X-axis direction. It is formed so as to be parallel to the axis. Such an elongated hole-shaped engaging hole 10a-
13a may be an assembly structure that includes a notch and a member that closes the notch.

Next, the operation of the vibration damping mechanism of this dehydration washing machine will be described with reference to FIG. When the outer tub 4 swings in the X-axis arrow direction due to imbalance during the spin-drying operation of this spin-drying washing machine, the swing causes the conversion lever 10 whose movement in the X-axis direction is restricted by the suspension rod 5 to be centered on the suspension rod 5. Then, it is rotated counterclockwise and converted into a vibration damping force acting on the outer tub 4 in the Y-axis arrow direction. When the outer tub 4 swings in the direction opposite to the X-axis, the swing causes the conversion lever 12 to rotate counterclockwise about the suspension rod 7 and acts on the outer tub 4 in the direction opposite to the Y-axis. Converted to vibration damping force. At this time, the conversion levers 11 and 13 move in the direction of the long sides of the engagement holes 11a and 13a with respect to such deflection of the outer tub 4 in the X-axis direction. It does not rotate like the conversion levers 10 and 12.

When the outer tub 4 swings in the direction of the Y-axis, the swing causes the conversion lever 13 whose movement in the Y-axis direction is restricted by the suspension rod 8 to rotate counterclockwise about the suspension rod 8. This acts on the outer tub 4 as a vibration damping force in the direction opposite to the X-axis. When the outer tub 4 swings in the direction opposite to the Y-axis, the swing causes the conversion lever 11 to rotate counterclockwise about the suspension rod 6 and acts on the outer tub 4 as a vibration damping force in the direction of the X-axis. To do. The conversion levers 10 and 12 are provided with engagement holes 10a,
Since it moves in the long side direction of 12a, the conversion lever 10,
12 does not rotate like the conversion levers 11 and 13.

The vibration damping action of the conversion levers 10 to 13 as described above exhibits a further excellent effect by making the conversion levers 10 to 13 faithfully follow the shake of the outer tub 4. As a means for improving the followability, as shown in FIGS. 4 to 6, means for utilizing magnetic force can be proposed.

In the example shown in FIG. 4, each conversion lever 10 to 13 is used.
Permanent magnets 21a, 21b, 22a on both sides of the outer tank 4 side,
22b, 23a, 23b, 24a, and 24b are provided, and the magnetic bodies 25 to 28 are installed on the outer periphery of the opposing outer tank 4.

In the example shown in FIG. 5, each conversion lever 10-13 is used.
The magnetic bodies 31a, 31b, 32a, 3 are provided on both sides of the outer tank 4 side.
2b, 33a, 33b, 34a, 34b are provided, and the permanent magnets 35-38 are installed on the outer circumference of the opposing outer tank 4.

In the example shown in FIG. 6, each conversion lever 10 to 13 is used.
The permanent magnets 21a to 24b and 35 to 38 are installed on both ends of the outer tub 4 and the outer circumference of the outer tub 4 so as to face each other with a polarity that generates attractive force.

According to such a configuration, each conversion lever 1
Since both ends of 0 to 13 are in a contact state in which both ends are attracted to the outer tub 4 by magnetic force, they sensitively react to a slight shake of the outer tub 4 to generate a vibration damping force.

The vertical positions of the conversion levers 10 to 13 installed on the hanging rods 5 to 8 are preferably on the outer tub 4 having a large amount of shake, and preferably above the central portion. The position.

In each of the above-mentioned examples, one conversion lever 10-13 is provided for each suspension rod 5-8, but a plurality of conversion levers are provided separately for each suspension rod 5-8 in the vertical direction. It is also possible to increase the effect by applying a vibration damping force to the outer tub 4 at a plurality of positions. Further, the conversion levers 10 to 13 of the integrated body are illustrated, but the same operation and effect can be obtained as a divided structure in which an action portion for the outer tub 4 and an engagement portion for the suspension rods 5 to 8 are separated. .

In this way, the deflection of the outer tank 4 is converted by the lever 10.
In the vibration damping mechanism section that transmits the vibration damping force to the to 13 to 13, the contact sound is generated from the contact portion between the outer tub 4 and the conversion levers 10 to 13, and the vibration sound is transmitted and causes the noise generation. .
In order to prevent the generation of the contact sound and the transmission of the vibration sound, it is possible to propose a means for interposing a cushioning member between the contact portions of the both.

In the example shown in FIG. 7, each conversion lever 10-13 is used.
Cushioning members 41a, 41b, 42a on both sides of the outer tank 4 side,
This is a configuration in which 42b, 43a, 43b, 44a, 44b are installed.

In the example shown in FIG. 8, each conversion lever 10 to 13 is used.
The cushioning members 45 to 48 are installed on the outer periphery of the outer tub 4 facing both ends of the.

In the example shown in FIG. 9, each conversion lever 10 to 13 is used.
Buffer members 41a to 44 on both ends of the outer tub 4 and on the outer periphery of the outer tub 4.
b, 45 to 48 are installed.

According to this structure, each conversion lever 1
Both ends of 0 to 13 are buffer members 41a with respect to the outer tank 4.
Since it touches via ~ 44b and 45-48, it is possible to prevent generation of contact noise and cut off transmission of vibration noise. By making the permanent magnet and the magnetic body in the above-described embodiment elastic, it is possible to achieve both the object of improving the followability and noise prevention.

Next, another embodiment of the present invention will be described with reference to FIGS. FIG. 10 is a partially developed vertical sectional side view of the dewatering washing machine in this embodiment, and FIG. 11 is a BB sectional view thereof. The same components as those in the above-described embodiment are designated by the same reference numerals, and duplicated description will be omitted.

Conversion levers 51 to 54 in the vibration damping mechanism section
Engage with the support members 55 to 58 hanging from the upper edges of the four corners of the outer frame 9 having high rigidity through the engagement holes 51a to 54a, and both ends thereof are ¼ arcs (90 degrees) of the outer circumference of the outer tub 4. It faces the outer tank 4 at a distant position. The engaging holes 55a to 58a are directionally formed in a rectangular shape in order to realize movement and rotation on a horizontal plane, as in the above-described embodiments.

Engagement holes 51a, 5 of the conversion levers 51, 53
The reference numeral 3a has a directivity that restrains the conversion levers 51 and 53 in the X-axis direction and allows free movement in the Y-axis direction.
Also, the engaging holes 52a, 54a of the conversion levers 52, 54
Has a directivity that allows the conversion levers 52 and 54 to freely move in the X-axis direction and restrains them in the Y-axis direction.

Also in this embodiment, when the outer tank 4 including the inner tank 3 is vibratingly displaced in the X-axis arrow direction, the conversion lever 5 is used.
1 rotates counterclockwise about the support member 55, and a force for pushing the outer tub 4 acts in the direction of the Y-axis arrow which is 90 degrees in phase in the rotational direction. As a result, a damping force proportional to the vibration displacement acts on the outer tub 4, and the vibration reducing effect of the dehydration washing machine can be obtained. At this time, since the conversion lever 54 can freely move in the X-axis direction due to the directivity of the engagement hole 54a, no rotational force is generated, and the conversion lever 5 does not move.
No effects occur because the outer tanks 2 and 53 are positioned away from each other.

When vibrations in other directions occur, the same action occurs and the vibration reducing effect is exerted.

In this embodiment, since the converting levers 51 to 54 are supported by the supporting members 55 to 58 which are not affected by the vibration of the outer tub 4, the converting levers 51 to 54 are resistant to slight vibration of the outer tub 4. Even in this case, the vibration damping force can be generated in a reliable manner.

Also in this embodiment, the conversion levers 51 to 5
Such as improvement measures using the magnetic force regarding the followability of No. 4, noise reduction measures using cushioning material, plural conversion levers installed on one support member 55 to 58, divided structure of direction changing members 55 to 58, etc. Modifications can be applied as well.

Next, still another embodiment of the present invention will be described with reference to FIGS. FIG. 12 is a partially developed vertical sectional side view of the dehydration washing machine in this embodiment, and FIG.
FIG. The same components as those in the above-described embodiment are designated by the same reference numerals, and duplicated description will be omitted.

The direction changing member in the vibration damping mechanism portion of this embodiment is fixed to the outer peripheral surface of the outer tub 4 and is located in the space of the four corners of the outer frame 9, and the projections 61 to face the suspension rods 5 to 8. 64
Composed of

Protrusions 61 to 64 facing the hanging rods 5 to 8
The opposite surface of is most desirably formed with an inclination of 45 degrees with respect to the tangential direction of the outer circumference of the outer tub 4. The length of the facing surface of each of the protrusions 61 to 64 in the direction intersecting with the hanging rods 5 to 8 is determined mainly from the allowable vibration displacement amount limited by the gap between the outer tub 4 and the outer frame 9. , Opposing hanging bars 5-8
A gap 65 to 68 having a predetermined size, which is determined from the allowable vibration displacement amount at the time of rated rotation, is provided between and. Each protrusion 6
The thickness of 1 to 64 in the vertical direction may be a thickness that is satisfactory in strength.

With this structure, the outer tub 4 is constrained so that it can move in a certain direction within the horizontal plane. That is, this directionality is determined according to the rotation direction of the inner tank 3, and when the rotation direction is from the X axis to the Y axis as shown in the figure, the protrusions 61 and 63 move in the X axis direction. Is restrained by the suspension rods 5 and 7, but has a directionality in which it can move freely in the Y-axis direction, and the protrusions 62 and 64 are restrained by the suspension rods 6 and 8 in movement in the Y-axis direction but in the X-axis direction. Is specified by the facing surface with the direction that it can move freely.

Further, the projection 6 facing the hanging rods 5 to 8
The positions of 1 to 64 in the up-down direction are preferably in the upper part where the shake amount is large, and are preferably in the positions above the central part.

In this embodiment, the outer tank 4 including the inner tank 3
Is about to vibrate more than the amount of the gap 65 in the X-axis arrow direction, the opposing surface of the protrusion 65 abuts and is restrained by the suspension rod 5, so that the outer tub 4 is centered on this suspension rod 5. It works like rotating counterclockwise. This movement is similar to the force that pushes the outer tub 4 in the Y-axis arrow direction, which is 90 degrees in phase in the rotational direction with respect to the whirling, and as a result, the outer tub 4 is proportional to the vibration displacement. As a result, the damping force acts, and the vibration reducing effect of the dehydration washing machine can be obtained. At this time, since the protrusions 62 and 64 can freely move in the X-axis direction due to the directionality of the facing surfaces, no rotational force is generated, and
Since the facing surface of the protrusion 63 moves in a direction away from the suspension rod 7, no influence occurs.

When a vibration displacement in another direction occurs, a vibration damping force is generated by the same action and a vibration reducing effect is exerted.

In addition, such a vibration damping action causes a large vibration displacement amount as when the resonance rotational speed is passed at the initial stage of the dehydration operation, and the opposing surfaces of the projections 61 to 64 have the hanging rod 5 at the opposite side.
It occurs when it touches ~ 8, and the amplitude is reduced. It does not occur in the state where the vibration displacement amount is small and the facing surfaces of the protrusions 61-64 do not contact the hanging rods 5-8 as in the rated operation.

In this embodiment, the protrusions 61 to 64 provided on the outer circumference of the outer tub 4 are opposed to the suspension rods 5 to 8 and abut when the outer tub 4 vibrates to generate a vibration damping force. A vibration reduction effect can be obtained with a simple configuration. Moreover, the hanging rod 5
8 to 8 and the protrusions 61 to 64 are installed by utilizing the spaces at the four corners of the outer frame 9, it is possible to suppress the size increase of the machine body.

Further, in this embodiment, one projection 61-64 is provided on the outer circumference of the outer tub 4 so as to face each of the suspension rods 5-8, but a plurality of protrusions 61-64 are provided for each suspension rod 5-8. By providing the protrusions side by side so as to face each other, it is possible to increase the effect.

FIGS. 14 and 15 show a modified example in which a collision vibration is prevented by filling a gap between the facing surfaces of the hanging rods 5-8 and the projections 61-64 with a buffer in this embodiment. ing.

In the modification shown in FIG. 14, the projections 61 to 64 are provided.
Of the suspension rod 5 by the buffer bodies 61a to 64a provided on the opposing surfaces of the
It is the composition which filled up the gap between ~ 8. The thickness of the cushioning bodies 61a to 64a in the vertical direction may be similar to the thickness of the protrusions 61 to 64.

The modified example shown in FIG. 15 has a structure in which the regions of the suspension rods 5 to 8 facing the facing surfaces of the protrusions 61 to 64 are covered with buffers 5a to 8a to fill the gap between them. is there. The thickness of the cushioning bodies 5a to 8a in the vertical direction may be similar to the thickness of the protrusions 61 to 64.

Furthermore, the suspension rods 5 to 5 in this embodiment are
8 and the protrusions 61 to 64 are required to face each other in such a manner that the opposing surface is constrained in the vibration displacement direction of the outer tub 4 and the movable surface is allowed to move freely.
7, the engagement grooves 61b to 64b or the engagement window 6
You may form so that the hanging rods 5-8 may be enclosed by 1c-64c.

Next, still another embodiment of the present invention will be described with reference to FIGS. FIG. 18 is a partially developed longitudinal side view of the dehydration washing machine in this embodiment, and FIG. 19 is its D-
It is a D sectional view. The same components as those in the above-described embodiment are designated by the same reference numerals, and duplicated description will be omitted.

The protrusions 71 to 74, which are the direction changing members in the vibration damping mechanism portion of this embodiment, are installed so as to avoid interference with the suspension rods 5 to 8, and protrude from the inner wall of the outer frame 9 to form the protrusions 71 to 74. The regulating members 81 to 84 are provided so as to face the facing surface of 74 through the gaps 75 to 78.

Each protrusion 71 facing the regulating members 81-84
The opposing surfaces of ~ 74 are, with respect to the tangential direction of the outer periphery of the outer tub 4,
Most preferably, it is formed with an inclination of 45 degrees. And
The length of the facing surface of each of the protrusions 71 to 74 in the direction intersecting with the regulating members 81 to 84 is determined mainly from the allowable vibration displacement amount limited by the gap between the outer frame 6 and the outer tub 4, and the regulation is performed. The sizes of the gaps 75 to 78 between the members 81 to 84 are determined from the amount of allowable vibration displacement during rated rotation. Each protrusion 71 to 7
The outer tank 4 may have a thickness in the vertical direction as long as the strength is satisfactory.

With this structure, the outer tub 4 is constrained so that it can move in a certain direction within the horizontal plane. That is, this directionality is determined according to the rotation direction of the inner tank 3, and when the rotation direction is from the X axis to the Y axis as shown in the figure, the protrusions 71 and 73 move in the X axis direction. Is restricted by the restricting members 81 and 83, but has a directivity in which it can move freely in the Y-axis direction, and the protrusions 72 and 74 are restricted by the restricting members 82 and 84 to move in the Y-axis direction, but in the X-axis direction. Movement is specified by the facing surface with a free direction.

The protrusions 71 to 71 provided on the outer peripheral surface of the outer tank 4
The upper and lower positions of the restricting members 81 to 84 provided on the inner wall of the outer frame 74 and the outer frame 9 are preferably such that the amount of shake is large, and are preferably above the central portion. In addition, the regulating member 81
The vertical lengths of up to 84 need to be long enough to accommodate changes in the vertical height of the outer tub 4 (protrusions 71 to 74) that fluctuates depending on the laundry, washing water, and the like.

In this embodiment, the outer tank 4 including the inner tank 3
Is about to oscillate in the X-axis arrow direction by more than the amount of the gap 75, the opposing surface of the protrusion 71 abuts against the regulation member 81 and is restrained. It works like rotating counterclockwise. This movement is Y which is 90 degrees in phase in the rotational direction with respect to whirling.
This is the same as the force that pushes the outer tub 4 in the axial arrow direction. As a result, a vibration damping force that is proportional to the vibration displacement acts on the outer tub 4, and the vibration reducing effect as a dehydration washing machine is obtained. can get. At this time, since the protrusions 72 and 74 can freely move in the X-axis direction due to the directivity of the facing surfaces, no rotational force is generated, and the facing surfaces of the protrusions 73 move in a direction away from the regulating member 83. No impact will occur.

When vibrations in other directions occur, the vibration damping force is generated by the same action and the vibration reducing effect is exerted.

In addition, such a vibration damping action increases the vibration displacement amount as when the resonance rotational speed is passed at the beginning of the dehydration operation, and the opposing surfaces of the protrusions 71 to 74 come into contact with the regulating members 81 to 88. Occurs, the amplitude is reduced, and the amount of vibration displacement is small as in the rated operation.
This does not occur in the state where the facing surface of No. 1 does not contact the regulating members 81 to 84.

Each protrusion 7 facing each regulating member 81-84
5 to 78 are each one, but each regulation member 81 to 8
It is also possible to increase the effect by arranging a plurality of protrusions in parallel with each other so as to face each other.

20 to 22 show a modification in which collision vibration is prevented by filling the gaps between the protrusions 71 to 74 and the regulating members 81 to 84 with a buffer in this embodiment. .

The modified example shown in FIG. 20 has a structure in which buffers 81a to 84a for filling the gaps are provided at the tips of the respective regulation members 81 to 84.

The modification shown in FIG. 21 has a structure in which buffers 71a to 74a for filling the gaps are provided on the facing surfaces of the projections 71 to 74, respectively.

Then, the modification shown in FIG.
To 74, and the cushioning members 71a to 74a and 81a to 84a provided at the tips of the restricting members 81 to 84 fill the gap.

In each of these modifications, each buffer 71 is
The dimensions of a to 74a and 81a to 84a are the projections 71 to 74.
The size of the facing surface or the moving range of the facing surface may be applied.

The shapes of the protrusions 71 to 74 are limited by the surfaces facing the regulating members 81 to 84, and the shapes of the other parts are determined by strength and productivity. That is just one example. The same applies to the regulating members 81 to 84, and the shapes other than the surfaces facing the protrusions 71 to 74 are determined by strength, productivity, and the like, and the shape shown in the drawing is only one example.

[0071]

According to the present invention, the whirling force of the outer tub is converted into the vibration damping force acting on the outer tub at the phase advance angle of 90 degrees by the direction changing member so that the vibration amplitude is suppressed to a small value. Vibration of the outer tub during dehydration can be reduced.

Moreover, since such a damping mechanism is installed by effectively utilizing the spaces formed between the outer tubs at the four corners of the outer frame, it is possible to prevent the size of the machine body from increasing.

[Brief description of drawings]

FIG. 1 is a partially developed vertical sectional side view showing an embodiment of a dehydration washing machine according to the present invention.

2 is a cross-sectional view taken along the line AA of the dehydration washing machine shown in FIG.

FIG. 3 is a cross-sectional plan view of a main part of the dehydration washing machine for explaining the vibration damping action of the dehydration washing machine shown in FIG.

FIG. 4 is a cross-sectional plan view of a main part of the dehydration washing machine showing a modified example of the dehydration washing machine shown in FIG. 1.

FIG. 5 is a cross-sectional plan view of a main part of the dehydration washing machine showing another modified example of the dehydration washing machine shown in FIG. 1.

FIG. 6 is a cross-sectional plan view of a main part of a dehydration washing machine showing still another modified example of the dehydration washing machine shown in FIG. 1.

FIG. 7 is a cross-sectional plan view of main parts of the dehydration washing machine showing still another modified example of the dehydration washing machine shown in FIG. 1.

FIG. 8 is a cross-sectional plan view of a main part of a dehydration washing machine showing still another modified example of the dehydration washing machine shown in FIG. 1.

FIG. 9 is a cross-sectional plan view of the main parts of the dehydration washing machine showing still another modified example of the dehydration washing machine shown in FIG. 1.

FIG. 10 is a partially developed vertical sectional side view showing another embodiment of the dehydration washing machine according to the present invention.

11 is a cross-sectional view taken along the line BB of the dehydration washing machine shown in FIG.

FIG. 12 is a partially developed vertical sectional side view showing still another embodiment of the dewatering washing machine according to the present invention.

13 is a cross-sectional view taken along line CC of the dehydration washing machine shown in FIG.

FIG. 14 is a cross-sectional plan view of main parts of the dehydration washing machine showing a modified example of the dehydration washing machine shown in FIG. 12.

FIG. 15 is a cross-sectional plan view of a main part of a dehydration washing machine showing still another modified example of the dehydration washing machine shown in FIG. 12.

16 is a cross-sectional plan view of a main part of a dehydrating washing machine showing still another modified example of the dehydrating washing machine shown in FIG.

FIG. 17 is a cross-sectional plan view of the essential parts of a dehydration washing machine showing still another modified example of the dehydration washing machine shown in FIG. 12.

FIG. 18 is a partially developed vertical sectional side view showing still another embodiment of the dehydration washing machine according to the present invention.

FIG. 19 is a cross-sectional view taken along line CC of the dehydration washing machine shown in FIG.

FIG. 20 is a cross-sectional plan view of the main parts of the dehydration washing machine showing a modified example of the dehydration washing machine shown in FIG. 18.

FIG. 21 is a cross-sectional plan view of the essential parts of the dehydration washing machine showing another modified example of the dehydration washing machine shown in FIG. 18.

22 is a cross-sectional plan view of essential parts of a dehydration washing machine showing still another modified example of the dehydration washing machine shown in FIG. 18. FIG.

[Explanation of symbols]

1 ... Balance ring, 2 ... Stirring blade, 3 ... Inner tank, 4
... Outer tank, 5-8 ... Suspension bar, 9 ... Outer frame, 10-13
... direction changing member, 10a to 13a ... engaging hole.

 ──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Tamotsu Kamori 1-1-1 Higashitaga-cho, Hitachi City, Ibaraki Prefecture Inside the Taga Headquarters, Hitachi, Ltd.Electrical Equipment Division (72) Inventor Hiroshi Osugi Hitachi, Higashi City, Ibaraki Prefecture 1-1-1 Tagacho Inside the Taga Headquarters, Hitachi, Ltd.Electrical Equipment Division

Claims (15)

[Claims] 1. A dewatering washing machine comprising an inner tub having a stirring blade at the center of the bottom, an outer tub enclosing the inner tub, and an outer frame elastically supporting the outer tub, wherein the outer tub is swung around. A dewatering washing machine provided with a vibration damping mechanism for generating a vibration damping force having a phase advance component of 90 degrees with respect to the displacement direction and acting on the outer tub. 2. The vibration damping mechanism according to claim 1, wherein the vibration damping mechanism is provided on the outer frame side so as to face the outer periphery of the outer tub, and rotates in response to the wobbling of the outer tub with respect to the wobbling direction. A dewatering washing machine comprising a direction changing member that generates a vibration damping force for pressing the outer tub in a direction of a phase advance angle of 90 degrees. 3. The vibration damping mechanism according to claim 1, wherein the vibration damping mechanism is provided at four corners in the outer frame so as to face the outer periphery of the outer tank.
Rotating in response to the shake of the outer tub, 9
A dewatering washing machine comprising a direction changing member for generating a vibration damping force for pressing the outer tub in a direction of a phase advance angle of 0 degree. 4. The direction changing member according to claim 2 or 3, wherein an intermediate portion of the direction changing member is movably or rotatably supported in a directional manner, and one end of the direction changing member is moved or rotated by responding to a shake of the outer tub. A dewatering washing machine having a conversion lever, the other end of which causes a vibration damping force having a phase advance component of 90 degrees with respect to the shake of the outer tub to act on the outer tub by the rotation. 5. The dewatering washing machine according to claim 1, wherein the inner tub is provided with a balance ring at an upper edge thereof. 6. A dehydration washing machine comprising an inner tub having a stirring blade at the center of the bottom, an outer tub enclosing the inner tub, and an outer frame supporting the outer tub with a hanging rod, wherein the outer tub comprises A vibration damping force that is provided on the suspension rod so as to face the outer circumference and rotates in response to the shake of the outer tank and presses the outer tank in the direction of the phase advance angle of 90 degrees with respect to the shake direction is applied. A dehydration washing machine comprising a direction-changing member for generating the dewatering. 7. The suspension bar according to claim 6, wherein the suspension rod is arranged in a space at four corners in the outer frame, and the direction changing member rotates or moves in response to the shake of the outer tub in the space, and the swing direction is changed. The dehydration washing machine is characterized in that the hanging bar is engaged so as to generate a vibration damping force for pressing the outer tub in a direction of a phase advance angle of 90 degrees. 8. The direction changing member according to claim 6 or 7, wherein an intermediate portion of the direction changing member is rotatably and rotatably supported, and one end of the direction changing member is rotated or moved by responding to a shake of the outer tub. A dewatering washing machine having a conversion lever, the other end of which causes a vibration damping force having a phase advance component of 90 degrees with respect to the shake of the outer tub to act on the outer tub by the rotation. 9. The dewatering washing machine according to claim 4, further comprising a magnet for bringing the facing portion of the outer tub and the conversion lever into an attracting state by a magnetic force. 10. The vibration damping mechanism according to claim 1, wherein the vibration damping mechanism is provided on the outer periphery of the outer tub, and moves with the vibration of the outer tub to come into contact with a member on the outer frame side to cause the vibration of the outer tub. A dehydration washing machine comprising a direction changing member that generates a vibration damping force in a direction having a phase advance angle of 90 degrees with respect to the direction. 11. A dehydration washing machine comprising an inner tub having a stirring blade at the center of the bottom, an outer tub enclosing the inner tub, and an outer frame supporting the outer tub with a hanging rod, wherein the hanging rod They are provided on the outer periphery of the outer tub so as to face each other, and act on the outer tub in a direction having a phase advance angle of 90 degrees with respect to the swing direction in response to the swing of the outer tub and contacting the suspension rod. A dewatering washing machine comprising a direction changing member that generates a vibration damping force. 12. The dewatering washing machine according to claim 10 or 11, wherein the direction changing member is provided so as to be located in four corner spaces in the outer frame. 13. A dewatering washing machine according to claim 11, wherein a buffer is interposed between the direction changing member and the hanging bar. 14. A dewatering washing machine comprising an inner tub having a stirring blade at the center of the bottom, an outer tub enclosing the inner tub, and an outer frame elastically supporting the outer tub, wherein A restricting member provided on the inner wall and an outer periphery of the outer tank are provided in contact with the restricting member in response to a shake of the outer tank and contact the restricting member in a direction of a phase advance angle of 90 degrees with respect to the shake direction. A dewatering washing machine comprising a direction changing member that generates a vibration damping force acting on an outer tub. 15. The dewatering washing machine according to claim 14, wherein a cushioning body is interposed between the direction changing member and the regulating member.