JPH10151295A - Electric washing machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the resonance amplitude of a specified oscillation mode and to reduce the size by changing the configuration of a hanging bar mechanism of a full automatic washing machine. SOLUTION: This dewatering/washing machine is provided with a balance body 12 as a hollow circular body containing fluid at its top end opening part and bottom part, an inner drum 5 containing an agitator blade at its bottom center, an outer drum 3 which connects an attaching plate 9 at its bottom to which a motor 8, clutch 7, and a belt drive transmission system are attached, and the outer drum 3 connects and contains the inner drum 5 through the clutch 7 and a flange 6, and an outer frame 1 supporting the outer drum 3 through the hanging bar, and the dewatering/washing machine performs both washing and dewatering at the inner drum 5. The hanging bar 2 mechanism contains at least one spring and a vibration absorber consisting of at least one weight and an attenuator.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

[0001] The present invention relates to an electric washing machine.

[0002]

2. Description of the Related Art A conventional hanging rod mechanism serves to suspend an outer tank made of synthetic resin, which includes an inner tank and fastens a power transmission system to a bottom, from four corners of an outer frame. Receiving
Although it has an anti-vibration function due to frictional attenuation between both the sliding ring and the sliding cylinder and is inexpensive and simple, it is not necessarily a structure having a necessary and sufficient anti-vibration function.

The following are known as related examples.

Japanese Patent Laid-Open Publication No. Hei 6-15091, "An anti-vibration device for a washing machine"

[0005]

In a fully automatic spin-drying washing machine, during a spin-drying operation, two critical speeds, a parallel mode and a conical mode, are passed during rotation start-up and rotation stop when stopped. In particular, at the time of startup, since there is a large unbalance and a large resonance amplitude phenomenon occurs, there is a problem that a conical mode having a high frequency is particularly difficult to pass due to its vibration form.

It is effective to make the gap between the outer frame and the outer tank narrower for the purpose of downsizing, and there is a problem that it is necessary to reduce the resonance amplitude.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a hanging bar mechanism structure and a compact large-capacity dehydrating washing machine having the same that can solve the above-mentioned problems and are inexpensive and simple, capable of passing low resonance amplitude with a conical mode. To provide.

[0008]

According to the present invention, at least one set of dynamic vibration absorbers is provided on a suspension rod mechanism to achieve the above object.

It is a suspension rod having a slider at one end and a slide ring containing a slide ring, a spring seat and a spring at the other end. A spring element, a mass body and an attenuator are provided between the slider and the slide cylinder. And a suspension rod mechanism characterized by comprising a dynamic vibration absorber constituted by the above vibration system.

The vibration system of the spring element, the mass body, and the damper constituting the dynamic vibration absorber has a configuration in which the vibration system has a single degree of freedom, and the natural frequency thereof is set to the natural frequency of the conical mode of the washing machine. The purpose of the present invention is to make them substantially coincide with each other and to provide appropriate attenuation.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS. 1, 2, 3 and 4. FIG. 1 is a longitudinal sectional view of a dehydration washing machine according to one embodiment. In this figure, only the hanging bar mechanism and the basic components of the washing machine, which are main components of the present invention, are described, and other components, such as a panel switch, are omitted and not shown. Its main components are an outer frame 1 and an outer tank 3 made of a synthetic resin elastically supported by the outer frame via a hanging rod 2. The outer tank is equipped with a stirring wing 4 to cancel imbalance. Tank 5, on which a fluid balancer 12 is mounted for mounting, a flange 6, which supports the inner tank on a clutch shaft, a clutch 7, which supports the flange, a clutch and a motor 8, which are held by an outer tank. A mounting plate 9, a capacitor 10 held by the mounting plate, and a pulley / belt system 11 for transmitting torque between a motor and a clutch. During washing, the agitating blades 4 are rotated during dehydration, and the inner tub 5 is rotated by a motor 8 through a clutch 7 via a pulley / belt system 11.

FIG. 2 is a longitudinal sectional view of the hanging bar mechanism. FIG.
As shown in the figure, the suspension rod mechanism of the present embodiment has a slider 13 at one end of the suspension rod 2 and a slide ring 14 at the other end of the suspension rod 2.
a, a spring seat 15 and a sliding cylinder 17a containing a spring 16a, and a spring 16b between the slider 13 and the sliding cylinder 17a.
And a weight 18 supported by the spring, a sliding ring 14b circumscribed by the weight, and a sliding cylinder 17b containing these. The relationship between the spring 16b and the weight 18 is selected so that the natural frequency of the one-degree-of-freedom system constituted by the spring and the weight substantially matches the natural frequency of the conical mode of the washing machine.

Next, the operation of the hanging bar mechanism will be described with reference to FIGS. 2, 3 and 4. FIG. In a spin-drying process, the washing machine generates a large unbalance due to an offset of the laundry in the inner tub at the start of rotation. Therefore, as shown in FIG. 3, at the time of resonance with the conical mode, a large whirling vibration of the sesame wobbling motion is generated. At this time, vibration in the direction along the hanging rod is transmitted to the hanging rod via the outer tank, and similar vibration is transmitted to the dynamic vibration absorber installed on the hanging rod. Also, the dynamic vibration absorber exhibits a resonance phenomenon because its natural frequency substantially matches the conical mode. Since the dynamic vibration absorber has a friction damping mechanism including a sliding cylinder and a sliding ring as shown in FIG. 2, a damping force is generated according to the movement of the weight due to resonance. As a result, the energy of the conical mode vibration of the washing machine is consumed by the dynamic vibration absorber, and the vibration amplitude of the washing machine is reduced. In order to achieve the maximum effect, the dynamic vibration absorber may be installed at the position where the vibration of the main system is maximum. In other words, it is on the outer peripheral side of the outer tub, but is most effective on the hanging rod in consideration of ease of installation and space efficiency as a washing machine.

FIG. 4 shows an example of analysis on the effect of reducing the amplitude of the dynamic vibration absorber, where the horizontal axis represents the dimensionless frequency and the vertical axis represents the response coefficient, and the relationship between the frequency and the response magnification is shown in FIG. Here, the dimensionless frequency is the value obtained by dividing the excitation frequency by the natural frequency of the main system, the response coefficient is the value obtained by dividing the response amplitude by the static displacement due to the excitation force, and the damping ratio is the damping of the system. Indicates the value divided by the critical damping.
When the washing machine is regarded as the main system and the dynamic vibration absorber is regarded as the auxiliary system, FIG. 4A shows the case of only the main system, and FIG. 4B shows the main system and the auxiliary system. Has a mass ratio of 0.04, a natural frequency ratio of the main system and the auxiliary system of 1.0, and a damping ratio of the main system of 0.1.
The case where the attenuation ratio of the auxiliary system is 0.3 is shown. As shown in FIG. 4, when there is a dynamic vibration absorber as an auxiliary system, it can be seen that the resonance response magnification of the main system is reduced to about 70% as compared with the case where only the main system is used. The amplitude reduction rate of the dynamic vibration absorber changes depending on the mass ratio of the main system and auxiliary system, the natural frequency ratio of the main system and auxiliary system, and the damping ratio of each system. You need to determine a numerical value. The attenuation ratio of the conventional hanging rod of the washing machine is approximately 0.1 or more, and the following description assumes that the attenuation ratio of the main washing machine is 0.1 or more.

When considering the weight of the washing machine, it is desirable that the mass of the dynamic vibration absorber be as small as possible. However, if it is too small, the vibration amplitude of the auxiliary system becomes too large, which causes a problem in strength. In a 7 kg washing machine, the mass ratio between the main system and the auxiliary system is preferably about 0.03 or more.

The natural frequency of the conical mode of the washing machine is
The natural frequency changes depending on the washing capacity. Ideally, the natural frequency of the dynamic vibration absorber should be exactly the same as the natural frequency of the conical mode of the washing machine, but practically, if it is in the range of about 0.8 times to about 1.2 times. The goal is achieved.
It is said that the JIS cloth weighs about twice as much as the dry cloth when passing the natural frequency of the conical mode at the start of spin-drying, and the 7 kg capacity machine is about 25 kg at no load and about 25 kg at rated load. It becomes 40 kg. If the natural frequency is determined at half the rated load, the natural frequency changes from 1.14 to 0.89 times between no load and rated load. That is, at the time of design, the natural frequency of the dynamic vibration absorber may be set so as to match the natural frequency at the time of the washing amount of half the rated washing capacity.

In the case of the mass ratio and the natural frequency ratio, the damping ratio of the dynamic vibration absorber is preferably about 0.3 or more so that the vibration amplitude of the dynamic vibration absorber does not become large.

As a result, the problem in the dehydrating operation of the fully automatic dehydrating washing machine is solved. The dynamic vibration absorber achieves a low resonance amplitude and facilitates passage through a resonance point. By making the clearance between the outer tub 3 and the outer frame 1 smaller by lowering the resonance amplitude, the washing machine can be made compact and large in capacity.

[0019]

According to the present invention, there are provided: Low resonance oscillation when passing through the conical mode resonance point is achieved.

2. As a result of the lower resonance amplitude, the gap between the outer frame and the outer tub is reduced, and a compact large-capacity washing machine can be provided.

3. A compact large-capacity washing machine can be provided, and an easy-to-use and easy-to-use washing machine can be provided.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a basic configuration of the present embodiment.

FIG. 2 is a longitudinal sectional view of a main part of the embodiment.

FIG. 3 is an explanatory diagram of a vibration mode.

FIG. 4 is an explanatory diagram of an effect obtained by an analysis example.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Outer frame, 2 ... Hanging rod, 3 ... Outer tank, 4 ... Stirring wing, 5 ...
Inner tank, 6 ... Flange, 7 ... Clutch, 8 ... Motor, 9 ...
Mounting plate, 10: condenser, 11: pulley / belt system,
12: fluid balancer, 13: slider, 14a, 14b
... Sliding ring, 15 ... Spring seat, 16a, 16b ... Spring,
17a, 17b: sliding cylinder, 18: weight.

Claims (1)

[Claims] 1. An inner tank having a stirring blade in the center of the bottom, an outer tank containing the inner tank, and a driving means for driving the inner tank and the stirring blade are supported and fixed to the bottom of the outer tank. An electric washing machine having a mounting plate having an outer frame supporting the outer tub via a hanging rod mechanism, wherein the hanging rod has a mechanism having a spring action and a damping action at one end and a slider at the other end. An electric washing machine comprising a suspension rod mechanism and a dynamic vibration absorber including at least one spring, at least one mass, and at least one damping mechanism.