JP2834839B2 - Dehydrator - Google Patents

Description

The present invention relates to a dehydrator.

(B) Conventional technology As a conventional example, in order to elastically support the outer tank in the main body,
Providing a vibration isolator between the main body and the upper and lower parts of the outer tank,
A horizontal shaft type drum is rotatably supported in the outer tub, and a drive motor for rotating the drum is provided at the outer bottom of the outer tub, and the drum is rotated at a high speed, so that the dewatering in the drum is performed. In a dehydrator that dehydrates things,
As means for supporting the outer tub, the outer tub is suspended and supported from the top of the main body via a spring, and the bottom of the outer tub and the bottom of the main body are connected by a shock absorber, which is disclosed in Japanese Utility Model Publication No. 63-8386. (D06F33 / 02).

In other words, in such a drum type dehydrator, the outer tub vibrates violently in the vertical direction due to the rotation of the drum about the horizontal axis, so that the outer tub is elastically deformed in the vertical direction by a spring or a shock absorber. Need to be supported.

(C) Problems to be Solved by the Invention In the conventional example, the vibration is attenuated by the expansion and contraction of the spring and the shock absorber, and the damping effect during rotation of the drum is good. This has a problem in that the damping effect of the drum is poor, the time required for the drum to reach a steady state becomes longer, and the dewatering performance decreases.

The present invention relates to improvement of a dehydrator and solves such a problem.

(D) Means for Solving the Problems In order to elastically support the outer tub in the main body, the present invention provides a vibration isolator between the main body and upper and lower portions of the outer tub, And a drive motor for rotating the drum in the outer tub is provided, and the outer tub is configured to have a lower portion having a larger weight than an upper portion. By rotating at a high speed, the object to be dehydrated in the drum is dehydrated. The vibration isolator generates an elastic body that expands and contracts when the outer tub vibrates, and generates a sliding resistance when the elastic body expands and contracts. The vibration isolator on the upper part of the outer tank has a larger vibration absorbing power than the vibration isolator on the lower part.

For example, if the elasticity of the upper and lower elastics is the same,
If the sliding resistance of the upper sliding body is reduced, the upper elastic body relatively expands and contracts better, so that the vibration absorbing power of the upper vibration isolator increases.

In addition, if the sliding resistance of the upper and lower sliding members is the same, if the expansion and contraction performance of the upper elastic member is increased, the vibration absorbing power of the upper vibration isolator increases.

(E) Action That is, a frictional force is exerted by the action of the sliding body in accordance with the expansion and contraction of the elastic body. In particular, this frictional force largely acts at the start of dehydration when the elastic body starts to expand and contract.

In the case of a dehydrator that suspends and supports the outer tub in the main body, it is possible that relatively heavy motors, solenoid valves, etc., have better stability when attached to the lower part of the outer tub. Of course, in this case, the lower part of the outer tub is heavier than the upper part, so that the lower part of the outer tub is harder to move and the upper part is easier to move.

Therefore, at the time of vibration, the upper part of the outer tub tends to have a larger amplitude, but by making the vibration absorbing power of the vibration isolator at the upper part of the outer tub larger than that of the vibration isolator at the lower part of the outer tub,
The upper and lower amplitudes become uniform.

(F) Example An example of the present invention will be described with reference to the drawings.

1 is a frame made of sheet metal, 2 is an outer tank formed of a synthetic resin in the shape of a horizontal axis drum, 3 is a horizontal support surface formed on the lower surface of the outer tank 2, and 4 is fixed to the support surface 3 It is an iron mounting plate. Reference numeral 5 denotes a horizontal axis type resin drum rotatably disposed in the outer tank 2, and a large number of through holes 6 are formed in the periphery thereof.

Numerals 7 are four sets of upper supports for elastically suspending and supporting the outer tub 2 from the upper four corners of the frame 1, and hooks hooked at one end to the upper four corners of the frame 1 as shown in FIG. A hook 7b formed with a portion 7a, an insertion opening 7c in the center, a recess 7d formed around the insertion opening 7c, and a lower spring receiver fixed to the other end of the hook 7b around the outer periphery.
7e, and hook portions 8 which are inserted through insertion ports 7c of the lower spring receiver 7e, and one end of which is provided at each of the upper four corners of the outer tub 2.
, A support rod 7f hooked to the other end of the support rod 7f, an upper spring receiver 7g locked to the other end of the support rod 7f, and a recess 7d between the upper spring receiver 7g and the lower spring receiver 7e. It consists of a spring A7h. Also,
The insertion opening 7c is filled with a lubricant.

The upper support 7 is connected to the spring A7h.
The vibration of the outer tub 2 is absorbed by the expansion and contraction of the outer tub 2 and the sliding resistance between the support rod 7f and the insertion opening 7c.

9 are four lower support members disposed between the mounting plate 4 and the four bottom corners of the frame 1, and springs B9a fixed to the mounting plate 4 and the frame in a tensioned state. An elastic cylinder 9b provided around the outer periphery of the spring B9a. Further, a lubricant is applied to the inner surface of the cylindrical body 9b.

The lower supports 9 are connected to the springs B9a.
The vibration of the outer tub 2 is absorbed by the expansion and contraction action of the spring B9a and the sliding resistance caused by the friction between the spring B9a and the cylinder 9b, and the elastic cylinder 9b prevents the spring B9a from buckling.

Reference numeral 10 denotes a cylindrical body integrally formed by projecting an upper portion of the outer tub 2 upward into a rectangular cylindrical shape, and thereby a clothing input port B11 is formed in the upper portion of the outer tub 2. Reference numeral 12 denotes an upper surface plate made of a synthetic resin fixed to the upper end of the frame 1. An operation portion 12a for housing electronic components and the like at a front edge portion, and a housing portion 12b for housing a water supply device and the like at a rear edge portion. A swelling is formed, and a rectangular clothing inlet A13 is opened in the center. Are various operation keys arranged on the upper surface of the operation section 12. Reference numeral 15 denotes a bellows-shaped rubber packing, by which the clothes input port A13 and the input port B11 are connected in a watertight manner. Reference numeral 16 denotes a safety cover that opens and closes the clothing slot A13, and reference numeral 17 denotes an upper cover that opens and closes the upper surface of the safety cover 16.

Now, the outer tub 2 is formed separately from only the rear wall 2a, and the rear wall 2a is fixed after the drum 5 is stored from the rear opening of the outer tub 2. Reference numeral 18 denotes a cylindrical portion integrally formed on the center of the rear wall 2a so as to protrude inward. Reference numeral 19 denotes a blower duct A integrally formed on the outer surface of the rear wall 2a. The cylindrical part
The wall surface 19a covering 18 is close to the cylindrical portion 18,
Here, a drum rear bearing 20 is fixed. A heater casing 21 is formed above the air duct A19, and a sheath heater A22 is provided therein. Two
Reference numeral 3 denotes an iron plate surrounding the heater A22 so as to prevent burning of dust or the like to the resin material.

Reference numeral 24 denotes an overflow port opened at half the height of the rear wall 2a, 25 denotes an overflow chamber integrally formed with the rear wall 2a, and an overflow chamber for leading out overflow from the overflow port 24, 26, 26 Is the overflow chamber 25
A pair of electrodes 27 disposed therein are air traps integrally formed at the lower portion of the rear wall 2a, and are connected to a water level sensor 28 disposed in the accommodation portion 12b via a pressure hose 29. I have. Reference numeral 30 denotes a circulation duct integrally formed at a position above the overflow level of the rear wall 2a, and a circulation port
It communicates with the inside of the outer tub 2 via 31. Reference numeral 32 denotes a blower fan provided in the circulation duct 30, and reference numeral 33 denotes a connection pipe connecting the circulation duct 30 and the blower duct A19.

34 is a drain port provided at the bottom of the outer tub 2; 35 is a drain hose for leading drainage from the drain port 34 to the outside of the machine; The bottom is connected via a flood hose 36. Reference numeral 36 denotes a drainage electric valve that opens and closes the drainage port 34.Reference numeral 38 denotes a dual water supply solenoid valve device provided in the housing portion 12b, and one water supply valve A38a is connected to the water supply hose A39 via a water supply hose A39. The other water supply valve B38b is connected to a connection port 40 formed in the cylindrical body 10, and is connected to the upper front corner of the outer tub 2 via a water supply hose B41. In other words, the water supplied from the water supply hose B38b falls along the inner surface of the front wall 2a of the outer tub 2 and reaches the drain port.

The water supply hose A39 has a rear half portion 39a held in the horizontal direction, and the rear half portion 39a is formed in a bellows shape, and when the outer tub 2 vibrates in the horizontal direction,
The latter half 39a of the water supply hose A39 expands and contracts accordingly.

Reference numeral 42 denotes a rectangular clothing inlet C which is long along the peripheral surface of the drum 5 and has a size substantially equal to that of the clothing inlet B11. 43 is the input port C42
This is a synthetic resin lid for opening and closing the cover.

Reference numeral 44 denotes a washing motor fixed to the mounting plate 4 via a mounting bracket A45, and reverses the drum 5 at a low speed during washing. 46 is a mounting bracket on the mounting plate 4
A dehydration motor fixed via B47 rotates the drum 5 in one direction at high speed during dehydration.

Thus, during the washing process, the washing motor 44
The drum 5 is repeatedly inverted at a low speed, and so-called tap washing in which the laundry in the drum 5 falls from above to below is performed. In the dehydrating step, the drum 5 is rotated in one direction at a high speed by the dehydrating motor 46 so that the drum 5 is rotated.
The laundry inside is dehydrated by centrifugal force.

As described above, in the present embodiment, the outer tub 2 is supported by the upper support 7 and the lower support 9 so that the amplitude of the outer tub 2 in the vertical and horizontal directions during dehydration, in particular, The amplitude at the time of startup becomes small, and vibration of the device main body can be suppressed.

That is, generally, the vibration suppressing force F of the vibration isolator is represented by F = m + c + kx + μp (1). Where m: mass, c: damping coefficient, k: spring constant,
μ: Coefficient of friction,: Acceleration,: Speed, x: Displacement, p: Normal force to friction surface.

Here, in the case of the upper support 7 and the lower support 9 of the present embodiment, the expansion and contraction force of the spring A7h and the spring B9a, and the force of the support rod 7f and the insertion opening 7c, and the spring B9a and the elastic cylinder 9b. Since the vibration is attenuated by the mutual frictional force, the above equation (1) is given by F = kx + μp (2) for both the upper and lower supports 7 and 9. Therefore, at the time of vibration suppression, μ acts greatly,
In particular, since the coefficient of static friction is larger than the coefficient of dynamic friction, the effect of suppressing vibration during orbit is extremely good. Furthermore, the elastic cylinder 9b of the lower support 9 has a restoring force against deformation,
It greatly contributes to the suppression of vibration in the left and right directions.

FIG. 7 and FIG. 8 demonstrate the above based on experiments.

FIG. 7 shows the amplitude characteristic with respect to time, and FIG. 8 shows the amplitude characteristic with respect to different loads. It can be seen that the amplitude amount is significantly suppressed in each case as compared with the conventional case.

Here, as a conventional example, one using a spring alone as an upper support and using a shock absorber as a lower support was adopted. According to such a conventional example, since the upper vibration suppression force F1 is only the expansion and contraction of the spring, from the above equation (1), F1 = kx (3), the lower vibration suppression force F2 indicates that the shock absorber has a lower speed. Since it responds to the change, F2 = c (4)

According to the equation (3), only the expansion and contraction of the spring is used, so that the damping time of the vibration is long, and the F2 is very small at the start-up when the speed is almost zero according to the equation (4), which theoretically agrees with the experimental value.

In the case of a vibration damping structure using a spring, as shown in FIG.
Although a resonance phenomenon occurs shortly after the start-up, in the present embodiment, since the frictional force is also acting, the degree of the resonance phenomenon is slow, the vibration is easily attenuated, and the time until the steady rotation is reached. It is short (t1 <t2).

FIG. 9 shows another example, in which the structure of the upper supports 7 is similar to that of the lower supports 9 and is provided with an elastic cylindrical body 49 around the outer periphery of a spring C48.

Further, in this embodiment, the sliding resistance A of the upper support 7 between the support rod 7f and the insertion port 7c or the sliding resistance A due to friction between the spring C48 and the cylinder 49, The relationship between the sliding resistance B due to the friction between the spring B9a and the cylindrical body 9b is set to A <B. The reason is as follows.

That is, when the outer tub 2 is divided into upper and lower parts with the axis center as a boundary, since relatively heavy things such as motors and valves are provided in the lower part, the upper part weight M1 <the lower part weight The relationship is M2.

Here, from the relationship of force = acceleration α × weight M, acceleration α
And the weight M are inversely proportional, and if the force is constant,
As the weight M increases, the acceleration α decreases.

Therefore, if upper weight M1 <lower weight M2,
Upper acceleration α1> lower acceleration α2.

On the other hand, since the amplitude (displacement amount) = ∬αdtdt (4), if the displacement amount of the upper part of the outer tank is L1 and the displacement amount of the lower part is L2, L1> L2, and the upper part of the outer tank has a larger displacement. try to.

Therefore, it is necessary to make the upper part of the outer tank absorb vibration better than the lower part of the outer tank. As described above, by setting the relationship of sliding resistance A <sliding resistance B, As a result, the spring A7h and the spring C48 easily expand and contract, and the vibration absorbing force of the upper support 7 increases.

As means for changing the sliding resistance, it is preferable to change the material of the lubricant or change the diameter of the insertion port 7c or the cylindrical body 49. In this embodiment, specifically, the sliding resistance A is (1000 ± 200) gr, and the sliding resistance B is (3500 ± 300) gr.

The following table shows the amplitude of the upper end of the frame 1 in the cases of sliding resistance A = sliding resistance B, sliding resistance A> sliding resistance B, and sliding resistance A <sliding resistance B during dehydration. In the case where the vibration absorbing force of the upper support 7 was increased as in the present embodiment, the vibration suppressing effect was large, and the vibration of the frame 1 was suppressed while the vibration was suppressed. It can be seen that the vibration sound (e.g., the resonance sound of the frame) that occurs with this can also be reduced.

In the embodiment, the vibration resistance is changed in order to increase the vibration absorbing force of the upper support 7. However, the spring constant of the spring A7h may be reduced or lengthened.

(G) Effects of the Invention According to the configuration of the dehydrator of the present invention, the vibration absorbing force of the vibration isolator at the upper part of the outer tub is made larger than the vibration absorbing force of the vibration isolator at the lower part of the outer tub. Because the lower part of the tank is heavier than the upper part, even if the upper part of the outer tank tries to swing more than the lower part, vibration is well absorbed by the vibration isolator at the upper part of the outer tank, Are equalized. Therefore, rattling and noise of the main body can be reduced.

[Brief description of the drawings]

FIG. 1 is a perspective view of a washing machine employing the dehydrator of the present invention, FIG. 2 is a side sectional view of the same, FIG. 3 is a rear view of the same main part, and FIG. , FIG. 5 is a front view showing the same main section, FIG. 6 is a cross-sectional view of the upper support, FIG. 7 and FIG.
The figure is a sectional view showing another embodiment of the upper support. 1 ... frame (body), 2 ... outer tank, 5 ... drum,
7 Upper support (vibration isolator), 7c Insertion port, 7f
… Supporting rod, 7h… Spring A, 9 …… Lower support (vibration isolator), 9a… Spring B, 9b, 49 …… Cylinder, 48…
… Spring C (7c, 9a, 48: telescopic body, 7c, 7f, 9f, 9b, 48, 4
9: sliding body), 46 ... dehydration motor.

────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yoshikazu Baba 2-18-18 Keihanhondori, Moriguchi-shi, Osaka Sanyo Electric Co., Ltd. (56) References JP-A-56-1558692 (JP, A) (58) Field surveyed (Int.Cl. ⁶ , DB name) D06F 37/22 D06F 49/00-49/06

Claims (1)

(57) [Claims] An anti-vibration device is provided between the main body and upper and lower portions of the outer tub so as to elastically support the outer tub in the main body, and a horizontal shaft type drum is rotatably provided in the outer tub. A support motor is provided for supporting and rotating the drum in the outer tub, and the outer tub is configured so that the weight of the lower portion is larger than that of the upper portion. Wherein the anti-vibration device has an elastic body that expands and contracts when the outer tub vibrates, and a sliding body that generates sliding resistance when the elastic body expands and contracts, A dewatering machine characterized in that the vibration isolator at the upper part of the outer tub has a larger vibration absorbing power than the vibration isolator at the lower part.