JPS5818118B2 - Fully automatic washing machine drive device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a drive device for a fully automatic washing machine.

In conventional fully automatic washing machines, washing is accomplished by rotating a pulsator placed at the bottom of the basket, and dehydration is accomplished by rotating the pulsator and basket at high speed.

In this case, it is desirable to lower the Palsafe rotation during washing due to problems such as cloth stains, and for dehydration, it is possible to strongly dehydrate by increasing the basket rotation speed as much as possible, so make a difference in the rotation speed between them. It is desirable that

In a fully automatic washing machine that is normally used, a washing pulsator of 350 to 450 r, p, m is the most efficient in terms of cloth damage and cleaning.

Regarding dehydration, if the basket diameter is 360 to 400 mm, the dehydration required by the customer can be obtained at 800 to 950 rpm.

In order to make this difference in rotation speed possible, conventionally two motors were used.
/ 4-pole or 4/8-pole structure that creates a difference in the rotation speed for washing and dehydration, a structure that has one pulley and belt each for washing and dehydration, and a gear reduction gear between the pulley and the pulsator shaft. A structure with means was proposed.

In the case of changing the number of poles of the motor, if two motors are used due to the windings, the motor becomes large and heavy to install in the washing machine. It is difficult to support it quantitatively, and a strong mounting part is required.

In addition, washing is performed on the side with a larger number of poles and dehydration is performed on the side with a smaller number of poles, which is disadvantageous in terms of weight and electricity.

In the case of two belts, unless the center distance between them is constant, the desired tension cannot be obtained, which may cause belt slip.

Furthermore, since a pulley and belt dedicated to washing is used during washing, and a pulley and belt dedicated to dewatering is used during dehydration, it is difficult to provide a mechanical switching device for both.

In the case of gear reduction, mechanical noise is unavoidable due to the accuracy of mechanical parts and assembly errors.In recent years, noise complaints regarding home appliances have become even stronger, and there is an urgent need to reduce noise.

An object of the present invention is to provide a 5-drive device for a fully automatic washing machine that can reduce noise and improve reliability.

Hereinafter, one embodiment of the present invention will be described. A plurality of outer frame receivers 9 are fixed to the upper part of the outer frame 1, and a hanging rod 5 is provided via a slider 8. There is a spring 6, and the outer tank holder slides between the part 7 and suspends the outer tank 2 elastically.

A clutch case 15 is fixed to the bottom of the outer tank 2 by bolts (not shown).

The clutch case 15 has a plurality of arms, and the outer ends of the arms are coupled to the outer tank 2.

The lower case 16 is attached to the clutch case 15 with screws 62.
is installed, as well as the drain valve 23 and the motor 3.
0 is fixed.

An upper ball bearing 58 and a hollow shaft seal 59 are press-fitted into the clutch case 15 and fixed thereto.

The lower ball bearing 51 is press-fitted into the lower case 16, and the coil collar 4 is removed by the operation of the drain valve 23.
9 and the brake lever (which engages the tarlatch lever and the brake band 65)
A fixed pin (not shown) is provided to rotatably support a pin (not shown).

The deceleration means described below includes a hollow shaft 13.

A hollow shaft 13 is fixed by a tightening nut 12 to the bottom of the basket 4 to which the basket reinforcing plate 31 is fixed.

The basket 4 is provided with a large number of dehydration holes 3, and a balance ring 10 filled with a suitable liquid is fixed to the upper end.

A pulsator 11 is provided at the inner bottom of the basket 4.

The pulsator shaft 39 includes shaft metals 37 and 31 and a shaft seal 3.
6 and is pivotally supported within the hollow shaft 13.

A tank cover 32 is fixed to the upper part of the outer tank 2.

Power is transmitted from the motor 30 to the pulley 17 via the pulley 19 and belt 18.

Adjusting legs 20 and fixed legs 21 are attached to the bottom of the outer frame 1.

The side of the outer frame 1 has a substantially circular hole, and a drain valve 23 is provided.
The drain hose 22 is arranged to communicate with the outside.

An air trap 24 provided at the bottom of the outer tank 2 is connected to an air tube 25 for pressure detection.

A control box 28 that houses electrical components such as a timer 29 and a top cover 26 that houses a lid 27 are fixed to the upper part of the outer frame 1.

Washing is performed by automatically reversing the motor 30 under the control of a timer 29 at regular intervals, for example, 26 seconds on and 3 seconds off.

As a result, rotational force is transmitted to the pulley 19, belt 18, and pulley 17.

The center part of the pulley 17 is connected to the corner joint 46 of the gear shaft 44.
The washer 63 and nut 64 engage the pulley boss 4.
7, gear shaft 44, gear shaft angle joint 4
Part 6: Reliably fixed to the step.

As a result, the rotation of the pulley 17 is transmitted to the pulley boss 47 and the gear shaft 44.

Since the coil collar 49 is locked by the clutch brake lever (not shown) and the clutch spring 48 is also locked, the clutch spring 48 becomes loose in response to the forward and reverse rotation of the pulley 17, and the clutch spring 48 becomes loose on the gear box 52 side. Does not transmit power.

Clutch spring 48 is connected to pulley boss 47 and gear box 52
It is wrapped between the bosses by its own repulsive force.

At the tip of the gear shaft 44, one drive tooth 45 is formed as a body and meshes with the large diameter gear 55 of the intermediate gear 54, the small diameter gear 56, and the pulsator shaft gear 41.

As a result, power is transmitted from the pulley 17 to the pulsator shaft 39, causing the pulsator 11 to rotate.

The rotation of the motor 30 is first decelerated between the pulley 19, the belt 18, and the pulley 17 (this ultimately decelerates the rotation of the motor 30).
The dewatering rotation speed is set to 800 to 950 rpm), and the gear reduction section provides the necessary deceleration for washing.

To dehydrate, release the coil collar 49 and release the clutch spring 4.
When the motor 30 is rotated in the direction in which the gear 8 is wound, the gear box 52, the gear drum 43, the hollow shaft 13, and the pulsator shaft 39 rotate together at high speed.

In this type of spring type clutch, the gap G between the gear box 52 and the pulley boss 47 is fatal.

The clutch spring 48 is used with a rectangular cross section wrapped around it.

A rectangular cross section is used because of its transmission stability.

Between the axial thickness of this rectangular cross section and the above-mentioned gap G,
Empirically, it is desirable to have a gap of 1/10 or 1/20 of the thickness; if the gap is larger than this, the pulley boss 4
There is a risk that the spring will be caught between the gear box 7 and the gear box 52 and locked.

In addition, if the gap is too narrow, there is a problem such as the gap widening due to seizure wear due to sliding between the gear box 52 and the pulley boss 47 during operation, so it is necessary to carefully select a material that is sufficiently hard and wear resistant. There is.

Therefore, the pulley boss 47 has two or more flat surfaces 77 on its inner diameter.
It is necessary to have a shaft hole that can be used as a corner joint having a circular portion 78 and a hole having an outer diameter that is approximately the same as the boss of the gear box 52, with less runout.

The hardness is required to be approximately the same as that of the clutch spring 48.

It is desirable to manufacture it from a hardened sintered alloy that satisfies these conditions.

By slightly impregnating the sintered hole with oil, the clutch spring 4
8. Sliding wear during washing is extremely reduced.

In addition, wear occurs in the gap between the abutting joint with the gear box 52 due to loads, etc., but this is greatly alleviated by sintering.

In short, for the pulley boss 47, the center hole is a hole with two or more flat parts and a circular part, and is used as a corner joint, and both ends are parallel planes, so that it can be used no matter which direction it is assembled. It is desirable to make it from a sintered alloy to improve wear resistance.

Next, the gap between the gear box 52 and the pulley boss 47 is set as follows.

That is, the length of the square joint 46 from the bottom of the collar of the drive gear portion 45 of the gear shaft 44 is set to the minimum tolerance dimension that can be mass-produced.

Press fit the gear box metal 61 into the gear box 52.

When the gear box metal 61 is initially manufactured, the outer diameter is determined by the press-fit portion 19 into the gear box 52 and the flange portion 79a, as shown in FIG.

The inner diameter side is made up of a large diameter 80, a transition part 81, and a small diameter part 82.

Since the inner diameter of the gear box 52 is reduced due to the influence of the craftsman, the inner diameter after the final press-fitting is set to have an appropriate clearance with respect to the gear shaft 44, taking this into consideration.

That is, the gear box metal 61 is made of a sintered oil-impregnated metal having a large diameter portion 80, a transition portion 81, and a small diameter portion 82 in anticipation of press-fitting.

The dimensional tolerance in the axial direction of the gear box metal 61 cannot be made very small if the gap is a problem due to its manufacturing method.

Therefore, when press-fitting the gear box metal 61 into the gear box 52, use a press-fitting mandrel with a length that is equal to the dimension from the bottom of the collar of the gear shaft 44 to the corner joint 46, minus the required gap. It is press-fitted so that it is flush with the end face, and the flange portion unrelated to the press-fitting is compressed and deformed in the axial direction.

As a result, there is no need to cut the flange of the gear box metal 61 to obtain the axial dimension after press-fitting, so that the sliding characteristics of the flange are not impaired.

That is, in order to obtain the gap G, it is possible to make the flange of the gear box metal 61 long in advance and compressively deform it during press-fitting, so that the dimensions up to the corner joint 46 can be accurately obtained.

Next, the gear drum 43 is a bottomed drum with an opening at the contact part with the gear box 52 side, and an insertion part is provided on the outer diameter part so that the brake band 76 can be attached thereto.

A plurality of pins 5'7 are provided in the bottomed part with notches 83 and are embedded integrally during molding.

The pin 57 extends slightly inward from the contact surface of the gear box 52 and supports the intermediate gear 54 axially.

For this reason, the dimensions of the center distribution between the pin 52 and the hollow shaft 13 can be easily determined, and it is possible to improve the reliability in terms of noise and life of the gear, and also to reduce the cost.

Further, the remaining space of the intermediate gear 54 is filled with lubricating oil.

Assemblability can be improved by making the pin 57 have a pin diameter and embedding depth that can withstand cantilever support.

Next, the intermediate gear 54 constitutes an externally toothed planet, and is composed of a large diameter gear 55 and a small diameter gear 56, and is made of synthetic resin.

In the first stage, the large diameter gear 55 meshes with the drive tooth 45 of the gear shaft 44.

The small diameter gear 56 meshes with the pulse gear 41 to constitute a second stage of meshing.

Considering the transmission force relationship, the transmission force of the second stage is naturally larger than that of the first stage.

For this reason, it is possible to make the meshing tooth width larger in the second row than in the first row, but as the axial dimension increases and the meshing length increases, the error in the tooth trace direction increases, so the meshing length is preferably shorter.

For this purpose, the size of the teeth of the intermediate gear 54 is made larger at the second stage than at the first stage.

That is, if the tooth size and the module defined are, for example, 1 module in the first stage, then 1.25 modules in the second stage.

This compensates for the reduction in load sharing and the reduction in strength per combined specific volume due to the use of a plurality of intermediate gears 54.

As a result, noise reduction can be achieved by using the intermediate gear 54 made of synthetic resin with a large damping rate.

Next, since a plurality of intermediate gears 54 are used, the large diameter gear 5
5 and the small diameter gear 56, it is necessary to match the teeth at one location during manufacture.

If only one intermediate gear 54 is used, there is no need to perform tooth alignment as a gear device, but if multiple intermediate gears 54 are used, the tooth traces of the large diameter gear 55 and small diameter gear 56 of the intermediate gear 54 should be adjusted. If you adjust the direction in one place,
Against this.

Drive gear 45E1. In relation to the pulsator shaft gear 41 and the pulsator shaft gear 41, the meshing between the intermediate gears 54 has an important meaning.

If an attempt is made to assemble the gear device regardless of the tooth alignment of the intermediate gear 54, the number of teeth of the large-diameter gear 55 and small-diameter gear 56 of the intermediate gear 54 will naturally be different, and the pitch between each tooth will also be different, making it impossible to assemble. Become.

In case it was assembled. If this happens, one of the intermediate gears 54 will receive the load, and there is a risk of damage.

For this reason, the assembly positional relationship between the large-diameter gear 55 and the small-diameter gear 56 needs to match among the plurality of intermediate gears 54.

We propose a new assembly and girder for this purpose.

That is, in the case where three intermediate gears 54 are used, it is sufficient to assemble the large diameter gear 55 and the small diameter gear 56 with the mating portion 67 where the tooth traces of the large diameter gear 55 and the small diameter gear 56 match toward the center as shown in FIG.

Of course. The drive gear 45 and the pulsator shaft gear 41 are
The number of teeth must be divisible by 3.

To perform such assembly, a yato 70 as shown in FIGS. 5 and 6 is used.

At this time, a mark hole 66 is provided in the intermediate gear 54.

, the mark hole 66 is provided in a portion that matches the dimension relationship with the mating portion 67 that was mated.

Yatoi 70 has center bushing 68 and combined bushing 69.
will be established.

The pitch between the center bushes 68 is the same as the pitch between the pins 57 of the drum 43.
The pitch matches the pitch of

This allows the pin to be inserted into the 57th section and
When only the parts are taken out, the intermediate gear 54 can be set at the aligned position within the drum 43.

Further, the center bushing 68 and the mating bushing 69 are provided with split portions 74 and 75 to facilitate elastic deformation.

The mark hole 71 provided in the Yatoi 70 is located between the three intermediate gears 54.
In the case of , it is triangular with its apex facing toward the toothing area.

The Yatoi 70 has a flange portion 73 and is effective as a grip during assembly.

As described above, the Yatoi 70 has the same number of center bushings 68 and matching bushings 69 for the plurality of intermediate gears 54, and is manufactured so that the pitch matches the pitch of the pins 57 of the drum 43, so it is easy to assemble. It can also be used to check tooth alignment after assembly.

Next, the pulsator shaft 39 and gear 41 are also connected by a square joint 40, and the movement between them is regulated in the axial direction by a stopper 42.

There are various types of shaft couplings, but since a group of gears made of synthetic resin are installed in the drum 43, it is undesirable for chips and foreign matter to get mixed in during assembly, so a non-processing coupling is required.

Therefore, by press-fitting in the axial direction, it is prevented from moving in the opposite direction.

For example, a commercially available bush-on-fix or the like may be used as the stopper 42.

As described above, according to the present invention, it is possible to provide a drive device that can reduce noise and improve reliability.

[Brief explanation of drawings]

The drawings show one embodiment of the present invention, and FIG. 1 is a sectional view showing the main parts, FIG. 2 is an enlarged sectional view of the main parts of FIG. 1, and FIG. 3 is an enlarged sectional view of the main parts of FIG. Figure 4 is a bottom view of the main parts, Figure 5 is a sectional view of the shaft used to assemble the main parts, Figure 6 is a diagram explaining the assembled state of the main parts, and Figures 7 and 8 are FIG. 9 is a cross-sectional view of the main parts shown in FIG. 8, showing the state in which the main parts are installed. 2... Outer tank, 4... Basket, 13
...Hollow shaft, 15.--Case, 17.
...Pulley, 39...Pulsator shaft, 4
1...Pulsator shaft gear, 43...Gear drum, 44...Gear shaft, 45...
Drive gear, 52...Gear box, 55...
...Large diameter gear, 57...pin.

Claims (1)

[Claims] 1. An outer frame, an exterior supported in vibration isolation within this outer frame, a basket provided in this outer tank, a pulsator provided in the inner bottom of this basket, and a hollow shaft fixed to the outer bottom of the basket, one end. a pulsator shaft having the pulsator fixed to the pulsator shaft and a pulsator shaft gear made of synthetic resin fixed to the other end;
□A gear drum fixed to the hollow shaft, a case fixed to the bottom of the outer tank and covering the outer periphery of the gear drum, a drive gear formed at one end, a pinwheel fixed to the other end, and supported by the case. a gear shaft; a gear box fixed to the gear drum; a gear box fixed to the gear drum; a gear box fixed to the gear drum; A drive device for a fully automatic washing machine, comprising: a small diameter gear made of synthetic resin; and a large diameter gear made of synthetic resin, which is formed integrally with the small diameter gear and meshes with the drive gear.