JPS6118480B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a drive device for a fully automatic washing machine.

[Prior art]

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 pulsator rotation speed during washing due to problems such as cloth staining, and for dehydration, it is possible to strongly dehydrate by increasing the basket rotation speed as much as possible, so there should be no difference in the rotation speed between them. It is desirable to attach it.

Normally, in the fully automatic washing machines we handle, the washing pulsator is most efficient at 350 to 450 rpm, considering the damage to the fabric and cleaning. Regarding dehydration, if the basket diameter is 360 to 400 mm, dehydration that is not used by customers can be obtained at 800 to 950 rpm.

In order to make this difference in rotation speed possible, conventionally, the motor was configured with 2/4 poles or 4/8 poles to create a difference in the rotation speed for washing and spin-drying, and a separate pulley was used for washing and spin-drying. , a structure with a belt, and a structure with a gear reduction means between the pulley and the pulsator shaft were proposed. In the case of changing the number of poles of a motor, if two motors are used due to the windings, the motor will become larger, making it difficult to support it due to its weight when attached to a washing machine, and the strength of the mounting part is also large. something is needed.

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. In addition, during washing, a pulley and belt exclusively for washing are used, and during dehydration, a pulley and belt exclusively for dehydration is used.
This makes mechanical switching devices difficult.
In the case of gear reduction, mechanical noise cannot be avoided due to the accuracy of mechanical parts and errors in combination. In recent years, complaints about noise caused by home appliances have become even stronger, and it is urgent to reduce noise.

[Purpose of the invention]

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

[Summary of the invention]

The gist of the present invention is to form a corner joint having two or more plane parts and a circular part in the lower part of the gear shaft, and form the plane part and the circular part with which the corner joint engages on the inner diameter side of the pulley boss. The pulley boss is made of a sintered alloy.

[Embodiments of the invention]

Hereinafter, one embodiment of the present invention will be described.
A plurality of outer frame receiving parts 9 are fixed to the upper part of the frame, and a hanging rod 5 is provided via a slider 8.
There is a vibration-proofing spring 6 which slides between the outer tank holder 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 connected to the outer tub 2. In the clutch case 15,
The lower case 16 is attached with screws 62, and the drain valve 23 and motor 30 are 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 5 is installed in the lower case 16.
1 is press-fitted and fixed, and a clutch lever (not shown) that engages with the clutch lever and brake band 65 that controls the disconnection of the coil collar 49 and clutch spring 48 by the operation of the drain valve 23,
A fixed pin (not shown) is provided for rotatable support. The deceleration means described below include
A hollow shaft 13 is included. Basket reinforcement plate 3
A hollow shaft 13 is fixed to the bottom of the basket 4 to which the hollow shaft 13 is fixed by means of a tightening nut 12.
The basket 4 has many dehydration holes 3,
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 is supported within the hollow shaft 13 using shaft metals 37 and 38 and a shaft seal 36.

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 outer frame 1 has a substantially circular hole on the side,
A drain hose 22 is connected to the outside through a drain valve 23. 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 for housing electric components such as a timer 29 and a top cover 26 for housing 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 fixed 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 portion of the pulley 17 engages with the corner joint 46 of the gear shaft 44, and the washer 63
It is securely fixed to the step between the gear shaft 44 and the gear shaft angle joint 46 with the nut 64 and the pulley boss 47. This allows pulley 1
7 rotation is caused by the pulley boss 47 and gear shaft 44.
is transmitted to. 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 when the pulley 17 is rotated in the forward or reverse direction, and power is transmitted to the gear box 52 side. do not. The clutch spring 48 is wound between the pulley boss 47 and the boss of the gear box 52 by its own repulsive force. A drive gear 45 is integrally formed at the tip of the gear shaft 44 and meshes with the large diameter gear 55 of the intermediate gear 54, and 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 decelerated between the first pulley 19, the belt 18, and the pulley 17 (this is ultimately set so that the dewatering rotation speed of the basket 4 is 800 to 950 rpm), Furthermore, the gear reduction section provides the necessary speed reduction for washing. For dewatering, when the coil collar 49 is unlatched and the motor 30 is rotated in the direction in which the clutch spring 48 is wound, the gear box 52, gear drum 43, hollow shaft 13, and pulsator shaft 39 rotate integrally at high speed. .

In this type of spring clutch, the gap G between the gear box 52 and the pulley boss 47 is critical. The clutch spring 48 is used with a rectangular cross section wrapped around it. A rectangular cross section is used for reasons such as transmission stability. Empirically, there is a gap between the axial thickness of this rectangular cross section and the above-mentioned gap G, which is 1/10 to 1/20 of the thickness.
It is desirable to provide a gap between the two, and if the gap becomes larger than this, there is a risk that the spring will become trapped between the pulley boss 47 and the gear box 52 and become 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 a shaft hole that can be used as a square joint with an inner diameter of two or more plane parts 77 and a circular part 78, and an outer diameter of the hole that is approximately the same diameter as the boss of the gear box 52. Something with less vibration is required. 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. If the sintered holes are slightly impregnated with oil, the sliding wear of the clutch spring 48 during cleaning will be 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 preferable 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 as follows. That is, the length of the corner 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 79 and the flange portion 79a into the gear box 52, 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 becomes smaller due to the influence of press-fitting into the gear box 52, the inner diameter after the final press-fitting is set so as 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 gearbox metal 61 into the gearbox 52, use a press-fitting mandrel with a length equal to the dimension from the bottom 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, in order to obtain the axial dimension after press-fitting, the gear box metal 61
Since there is no need to perform operations such as cutting the flange, 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 determined.

Next, the gear drum 43 is a bottomed drum with an opening at the contact part with the gear box 52 side, and has an insertion part on its outer diameter part so as to snap the brake band 76 thereon. There are multiple pins 5 on the bottomed part.
7 is provided with a notch 83 and is embedded integrally during molding. The pin 57 is inserted slightly inward from the contact surface of the gear box 52 and is attached to the intermediate gear 54.
is supported by the shaft. For this reason, the center distribution dimension between the pin 52 and the hollow shaft 13 can be easily made constant, 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. pin 57
Assemblability can be improved by having a pin diameter and burial 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. The first stage is a large-diameter gear 55 that meshes with the drive teeth 45 of the gear shaft 44. The small diameter gear 56 meshes with the pulsator shaft gear 41 2
Configure the mesh of the tiers. 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 stage than in the first stage, but as the axial dimension increases and the meshing length increases, the error in the tooth trace direction becomes larger, so the meshing length should be increased. The shorter the length, the better. 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. In other words, if the module that defines the tooth size is, for example, 1 module in the first stage, then the module in the second stage is 1.25.
Make it modular. 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, it is necessary to match the teeth of the large diameter gear 55 and the small diameter gear 56 at one point 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 the directions are aligned in one place, the gear alignment between the intermediate gears 54 becomes important in relation to the drive gear 45 and the pulsator shaft gear 41. If you try to assemble the gear device regardless of the tooth alignment of the intermediate gear 54, the large diameter gear 55 and the small diameter gear 56 of the intermediate gear 54
Naturally, the number of teeth is different, and the pitch between each tooth is also different, making it impossible to assemble. If it were to be assembled, one of the intermediate gears 54 would bear the load and there is a risk of damage. For this,
The assembly positional relationship between the large diameter gear 55 and the small diameter gear 56 is as follows:
It is necessary to match 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. Naturally, the drive gear 45 and the pulsator shaft gear 41 need to have a number of teeth that is divisible by three.

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 whose dimensions match that of the mating portion 67 that was mated.

The Yatoi 70 is provided with a center bushing 68 and a mating bushing 69. The pitch between the center bushes 68 is made to match the pitch of the pins 57 of the drum 43. As a result, by inserting it into the pin 57 and pulling out only the Yato 70, the intermediate gear 54 can be set at the aligned position within the drum 43. Further, the center bush 68 and the mating bush 69 are provided with split portions 74 and 75 that facilitate elastic deformation. In the case of three intermediate gears 54, the mark hole 71 provided in the Yatoi 70 has a triangular shape so that its apex faces the mating portion. The Yatoi 70 has a flange portion 73 and is effective as a grip during assembly.

In this way, the Yatoi 70 has a plurality of intermediate gears 5.
4 has the same number of center bushings 68 and matching bushings 69, and the pitch is also the same as the pin 57 of the drum 43.
Since they are manufactured to match the pitch of the teeth, they can be used for assembly, drilling, and checking the alignment after assembly.

Next, the pulsator shaft 39 and gear 41 are also connected to the square joint 40.
, and the movement in the axial direction is regulated by a stopper 42 between them. 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, commercially available push-on fixes or the like may be used as the stopper 42.

The gear shaft 44 is supported by the gear box 52 via the gear box metal 61, the pulley boss 47 is attached to the lower side of the gear shaft 44, the clutch spring 48 is wound around the outer periphery of the gear box 52 and the pulley boss 47, and the outer periphery of the clutch spring 48 is By attaching a coil collar 49 to and locking it to the clutch spring 48, and locking the coil collar 49 from the outside, the clutch spring 48 is held in a loosened state against forward and reverse rotation of the pulley boss 47.
In a drive device for a fully automatic washing machine in which the loose state of the clutch spring 48 is released by releasing the coil collar 49 from the outside, a gap G is provided between the lower end of the gear box 52 and the upper end of the pulley boss 47, and the gear A joint with a flat part is formed on the lower side of the shaft 44, a shaft hole into which this joint is inserted is formed in the pulley boss 47, a flat part is also formed in this shaft hole, and the pulley boss 47 is made of sintered alloy. This is what I did.

According to this configuration, the following actions and effects can be expected.

(1) Since the gap G is provided between the lower end of the gear box 52 and the upper end of the pulley boss 47, friction between the gear box and the pulley boss does not occur. This reduces noise and prevents seizure due to friction.

(2) The gear shaft 44 and the pulley boss 47 are connected by a joint having a flat surface of the gear shaft 44 and an axial hole of the pulley boss 47 having a flat surface.

It is also conceivable to connect the gear shaft 44 and pulley boss 47 with a pin without fitting the joint with the flat part and the shaft hole with the flat part, but this has the following disadvantages. One is that pin-based connections are weak in strength. Another reason is that the pulley boss 47 is made of a sintered alloy and is therefore hard, making it difficult to machine the pin insertion hole.

The present invention can eliminate such problems.

(3) When the coil collar 49 is locked from the outside to hold the clutch spring 48 in a relaxed state and the pulley box 47 is rotated forward or backward, the outer periphery of the pulley boss 47 repeatedly slides against the inner periphery of the clutch spring 48. During this sliding, the end face of the pulley boss 47,
That is, the opposing end surface of the gear shaft 44 strongly rubs against the coil spring 48.

That is, the gear shaft 44 and the pulley boss 4
Since there is a gap G between coil spring 48 and
tends to flex inwardly, and since the coil spring 48 typically has a rectangular cross section, it tends to bite the opposing end surfaces. If the pulley boss 47 is made of ordinary steel, the opposing end surfaces will be crushed and the coil spring 48 will be more deflected. If this continues, it will cause malfunction. However, in the present invention, since the pulley boss 47 is made of a sintered alloy, it is harder than ordinary steel.
For this reason, the opposing end faces are not crushed due to galling as described above, and malfunctions do not occur.

[Brief explanation of the drawing]

The drawings show one embodiment of the present invention, and FIG. 1 is a vertical sectional view of the main part, FIG. 2 is an enlarged sectional view of the main part of FIG. 1, and FIG. 3 is an enlarged sectional view of the main part 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 9 is a cross-sectional view of the main parts shown in FIG. 8, showing a state in which the main parts are attached. 2... Outer tank, 4... Basket, 13... Hollow shaft, 15... Case, 17... Pulley, 39...
Pulsator shaft, 41...Pulsator shaft gear, 43
... Gear drum, 44 ... Gear shaft, 45 ... Drive gear, 52 ... Gear box, 55 ... Large diameter gear, 56 ... Small diameter gear, 57 ... Pin.

Claims (1)

[Claims] 1. The gear shaft 44 is supported by the gear box 52 via the gear box metal 61, the pulley boss 47 is attached to the lower side of the gear shaft 44, and the clutch spring 48 is attached to the outer periphery of the gear box 52 and the pulley boss 47. By wrapping the coil collar 49 around the outer periphery of the clutch spring and locking it to the clutch spring 48, and locking the coil collar 49 from the outside, the clutch spring 48 is held in a loosened state against forward and reverse rotation of the pulley boss 47. , in a drive device for a fully automatic washing machine that releases the loose state of the clutch spring 48 by releasing the lock from the outside of the coil collar 49, a gap G is provided between the lower end of the gear box 52 and the upper end of the pulley boss 47; A joint with a flat part is formed on the lower side of the gear shaft 44, and a shaft hole into which this joint is inserted is formed in the pulley boss 47. A flat part is also formed in this shaft hole, and the pulley boss 47
A drive device for a fully automatic washing machine, characterized in that it is formed of a sintered alloy.