JP3239091B2 - Washing machine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to a washing machine.
In particular, the present invention relates to a speed reduction mechanism for a washing / dewatering tub and a stirring blade.

[0002]

2. Description of the Related Art In a washing machine, generally, only the stirring blades in the washing and dewatering tub are driven at a low speed during washing and rinsing, and during washing and rinsing, the inner tub and stirring blades in the washing and dewatering tub are generally used. Are driven at high speed. The speed reduction mechanism for this purpose has a planetary gear mechanism that transmits the driving force from the motor to the stirring blade, and a hollow shaft that is provided outside the planetary gear mechanism and transmits the driving force from the motor to the inner tank. are doing. In the hollow shaft, the transmission of the driving force from the motor is interrupted by the clutch mechanism, and the rotation is stopped by the brake mechanism. The brake mechanism has an annular brake drum constituting a part of a hollow shaft, and an internal gear of a planetary gear mechanism is connected to the inside of the brake drum so as to be integrally rotatable.

The following is known as a connection structure between a brake drum and an internal gear. The two members, the brake drum and the internal gear, are formed in a cup shape that fits into each other, and the cup-shaped bottom portions are connected by uneven fitting. In the internal gear of this structure, the gear teeth on the inner peripheral surface and the concave / convex fitting portion on the bottom surface are separated in the axial direction, so that when the stirring blade is overloaded,
In some cases, the internal gear is twisted and deformed to generate gear noise due to meshing with the gear teeth of the internal gear.

[0004] Both members of the brake drum and the internal gear are formed in a ring shape, and keys are fitted into both key grooves of the key groove on the inner peripheral surface of the brake drum and the key groove on the outer peripheral surface of the internal gear. Structure where members are connected. In this structure, since the brake drum and the internal gear are connected to each other at the peripheral surfaces, the above-described problem can be prevented. On the one hand, the keyways make it easier for the brake drum to partially deform and the brake drum tends to deform unevenly. As a result, the accuracy of the shape of the brake drum, such as roundness, may be reduced, and the brake shoe may hit the outer peripheral surface of the brake drum during the braking operation, thereby causing brake noise.

In order to avoid the occurrence of such brake noise and gear noise, it is conceivable that the brake drum and the internal gear are formed thick so as not to be deformed. It is feared to invite.
An object of the present invention is to solve the technical problems as described above, with a washing machine for the speed reduction mechanism capable of preventing noise wash
Is to provide a machine .

[0006]

In order to achieve the above object, a washing machine according to the first aspect of the present invention comprises an outer shaft connected to a dewatering tub and integrally rotating, and an inner shaft connected to a stirring blade and integrally rotated. In a washing machine including a shaft, a ring-shaped internal gear provided inside the outer shaft, and a gear mechanism that rotates while meshing with the internal gear and has a planetary gear connected to the inner shaft, the internal gear includes an outer shaft. It is formed separately from the internal gear, and has serrations on the outer peripheral surface while having gear teeth meshing with the planetary gear on the inner peripheral surface of the internal gear, and has an inner peripheral surface of the outer shaft with respect to an outer peripheral surface of the internal gear. In order to prevent slippage, the internal gear has serrations that engage with the outer peripheral surface of the internal gear.
It is characterized by being serrated and engaged with the outer shaft .

According to this configuration, the following operation is achieved.
That is, the serrations on the outer peripheral surface of the internal gear and the serrations on the outer peripheral surface of the outer shaft engage with each other, so that the outer shaft and the internal gear can rotate integrally. For example, during washing and rinsing, the rotation of the dehydration tub and the outer shaft is stopped, and the inner shaft and the stirring blade are rotated via the gear mechanism. In addition, during dewatering, the internal gear and the planetary gear rotate integrally with the outer shaft, whereby the dewatering tank and the stirring blade rotate at high speed together.

In addition, since the load applied to the internal gear can be dispersed by serration engagement over the entire circumference, deformation of the internal gear at the time of driving transmission can be prevented, and gear noise when the internal gear and the planetary gear mesh with each other is reduced. be able to. Further, since the serrations on the inner peripheral surface of the outer shaft are formed in a waveform over the entire circumference, it is possible to prevent the outer shaft from being deformed unevenly. As a result, the outer shaft can be made thinner and inexpensively manufactured. .

A washing machine according to a second aspect of the present invention provides a washing machine according to the first aspect.
In the described washing machine , the serrations of the outer shaft and the inner gear are involute serrations. According to this configuration, the following operation is achieved in addition to the operation of the invention according to claim 1. That is, serrations can be easily and accurately processed over the entire circumference. Therefore, uneven deformation of the internal gear and the outer shaft can be reliably prevented, and gear noise can be reliably prevented.

[0010] Further, by engaging the entire circumference with high precision in this way, the load applied to the outer shaft can be surely dispersed over the entire circumference and reduced, so that the outer shaft can be reliably thinned. Thus, the outer shaft can be manufactured at lower cost. Washing machine of the invention according to claim 3, washing of claim 1 or 2, wherein
In the machine , the internal gear is formed of resin.

According to this structure, in addition to the function of the invention described in claim 1 or 2, the internal gear is made of resin, so that the gear noise is further reduced when meshing with the planetary gear. Can be. The washing of the invention according to claim 4
The machine is the washing machine according to any one of claims 1 to 3, wherein the washing, in order to stop the rotation of the dehydration tub during rinsing,
A brake member that winds around the outer peripheral surface of the outer shaft is provided.

According to this configuration, in addition to the operation of the invention according to any one of the first to third aspects, the serrations on the inner peripheral surface of the outer shaft are formed in a waveform over the entire circumference, so that the outer shaft has a serrated shape. Since the deformation can be prevented from becoming non-uniform, the shape accuracy of the outer peripheral surface of the outer shaft can be maintained. As a result, it is possible to prevent brake noise due to a one-sided contact when the brake member is wound around the outer peripheral surface of the outer shaft. . In particular, when the serration is an involute serration, uneven deformation of the outer shaft can be reliably prevented, and brake noise can be reliably prevented.

[0013]

[0014]

[0015]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment of the present invention will be described.
This will be described in detail with reference to the accompanying drawings. FIG. 1 is a side sectional view of a schematic configuration of a washing machine provided with a speed reduction mechanism for a washing machine according to an embodiment of the present invention. The washing machine is provided with a box-shaped housing 1, an outer tub 2 supported by a hanging rod (not shown) as a washing and dewatering tub inside the housing 1, and rotatably provided in the outer tub 2. An inner tub 3 is provided as a dehydration tub having a large number of small holes 3a on the surface. A water supply mechanism including a water supply valve 7, a pipe 5, and the like is provided at an upper portion in the housing 1, and the cleaning water is supplied to the inside from a pipe 6 connected to a water supply facility (not shown) such as an external water supply. . Wash water is stored in the outer tub 2, and laundry is stored in the inner tub 3. Inner tank 3 and stirring blade 11 provided at the bottom in inner tank 3
Are driven by the driving device 12. During washing and rinsing, only the stirring blade 11 rotates in one or both directions, and during dehydration, both the stirring blade 11 and the inner tub 3 rotate in one direction at high speed. Wash water after washing is drained through a drain valve 10 and a pipe 9.

The driving device 12 includes a motor 1 as a driving source.
3 and a small pulley 1 connected to the output shaft 14 of the motor 13
5, a large pulley 18, a belt 19 wound around the large pulley 18 and the small pulley 15, and a reduction mechanism for transmitting the rotation of the motor 13 transmitted by the belt 19 to the inner tank 3 and the stirring blade 11. And a bearing portion 16 as a bearing.

A drive shaft 17 is provided below the bearing 16 and is connected to a large pulley 18 to receive the driving force of the motor 13. A hollow support shaft 20 and an inner shaft 21 coaxially arranged at the center of the support shaft 20 are rotatably supported on the upper portion of the bearing portion 16. The support shaft 20 is connected to the bottom surface of the inner tank 3. Also, the inner shaft 21
Is connected to the stirring blade 11.

FIG. 2 is a partially sectional front view of the bearing portion.
FIG. 3 is a partial cross-sectional bottom view of the bearing portion. Bearing part 16
The upper bearing 2 press-fitted and fixed to the bottom surface 2a of the outer tank 2
2 and an oil seal 23. The upper bearing 22 and the oil seal 23
0 is held in a watertight and rotatable manner. An inner shaft 21 is rotatably inserted into the support shaft 20.

The bearing 16 is further provided with a gear case 24 fixed to the lower end of the support shaft 20 and provided in the gear case 24 to reduce the driving force of the motor 13 input from the drive shaft 17 to reduce the driving force of the inner shaft. A gear mechanism 25 for transmitting to the
It has a clutch mechanism 26 for transmitting / cutting off the driving force of the motor 13 input from the drive shaft 17 to the support shaft 20 and a brake mechanism 27 for stopping the rotation of the inner tank 3.

The gear case 24 is loosely fitted to the drive shaft 17 and an upper gear case 30 having a small diameter portion 28 fitted and fixed on the outer periphery of the support shaft 20 and a large diameter portion 29 surrounding the side of the gear mechanism 25. A lower gear case 33 having a cylindrical portion 31 and a flange portion 32 projecting outward from an upper end of the cylindrical portion 31. The flange portion 32 of the lower gear case 33 is coupled to the lower end of the large-diameter portion 29 of the upper gear case 30 so that the support shaft 20 and the gear case 24 can be rotated integrally. That is, in this embodiment, the support shaft 20 and the gear case 24 form a hollow outer shaft for driving the inner tank 3. The periphery of the gear case 24 is surrounded by a bearing cover 35 fixed to the lower surface of the outer tub 2 with bolts 34, and the lower gear case 33 is rotatable by a lower bearing 36 fixed to the bearing cover 35. Is held.

The gear mechanism 25 includes a sun gear 37 fixed to the upper end of the drive shaft 17, an internal gear 38 connected to the inner peripheral surface of the large diameter portion 29 of the upper gear case 30, and a sun gear 37.
And a planetary gear 39 that meshes with the internal gear 38 and rotates around the sun gear 37. Planetary gear 39
Is a gear holder 40 having one end fixed to the lower end of the inner shaft 21.
It is rotatably held by. Also, the internal gear 38
Is provided inside the large diameter portion 29 and is formed separately from the large diameter portion 29.

The brake mechanism 27 has an upper gear case 3
0, a brake drum having a large diameter portion 29, a brake band 48 bent substantially in a U shape along the outer peripheral surface of the brake drum, and a brake band 48 attached to a contact surface of the brake band 48 with the brake drum. A brake shoe 49 and a brake lever 50 rotatably supported by the swing shaft 47 and interlocking with the clutch mechanism 26 are provided. The brake band 48 has one end fixed to the bearing cover 35 by a bolt 51 and the other end locked to a brake lever 50.

A swing shaft 47 for supporting the brake lever 50
Is provided with a brake spring 52 as an urging means, and the elastic force of the brake spring 52 urges the brake lever 50 in a direction in which the brake band 48 is pulled. That is, in a normal state, the brake band 48 is pulled by the brake lever 50, the brake shoes 49 tighten the brake drum from the surroundings at the contact surface, and the brake shoes 49 come into close contact with the contact surface on the outer peripheral surface of the brake drum. The rotation of the brake drum is stopped. As shown in FIG. 3, when the brake lever 50 is displaced from the state shown by the solid line to the state shown by the two-dot chain line and the brake band 48 is loosened, the braking of the upper gear case 30 is released, and the upper gear case 30 is released. 30 is in a free rotation state.

During the washing step and the rinsing step, the brake shoe 49 is in close contact with the outer peripheral surface of the brake drum, and the brake drum is braked. Also, the clutch mechanism 2
6 is released, the rotation of the drive shaft 17 is not transmitted to the lower gear case 33, and the inner tub 3 does not rotate. On the other hand, the rotation of the drive shaft 17 is transmitted to the planetary gear 39 via the sun gear 37 fixed to the drive shaft 17. At this time, since the upper gear case 30 to which the internal gear 38 is connected is being braked, the planetary gear 39 revolves around the sun gear 37 while meshing with the internal gear 38. The revolution of the planetary gear 39 is transmitted to the inner shaft 21 via the gear holder 40, and rotates the inner shaft 21 at low speed. This allows
The stirring blade 11 fixed to the inner shaft 21 is rotated at a low speed.

At the time of the spin-drying process, the brake band 48 is loosened, the driving mechanism is connected by the clutch mechanism 26, and the driving shaft 17 and the lower gear case 33 are connected.
Accordingly, the driving force of the motor 13 is input to the drive shaft 17 and transmitted to the support shaft 20 via the gear case 24,
The inner tank 3 is rotated at a high speed. At this time, since both the drive shaft 17 and the upper gear case 30 are rotated at the same speed, the planetary gear 39 is revolved around the sun gear 38 at the same speed as the drive shaft 17. As a result, the inner shaft 21 is rotated at a high speed at the same speed as the upper gear case 30, and the stirring blade 11 fixed to the inner shaft 21 is rotated at a high speed. That is, at the time of the dehydration process, the inner tank 3 and the stirring blade 11 are integrally rotated at a high speed.

The internal gear 38 and the brake drum are connected to each other by the following connection structure. FIG. 4 is an exploded perspective view of a main part of a bearing of the washing machine. FIG. 5 is an enlarged sectional view of a main part of the connection structure of FIG. The connection structure is composed of, for example, a pair of serrations that engage with each other, more specifically, an involute serration, in which a pair of protrusions and recesses are fitted to each other. That is, the outer peripheral surface of the internal gear 38 is fitted into the inner peripheral surface of the brake drum, and the corrugated teeth 38 a are formed as projections on the outer peripheral surface of the internal gear 38, and are formed on the inner peripheral surface of the brake drum. A concave portion is defined between the corrugated teeth 29a, and the concave portion and the convex portion are engaged with each other in a fitted state. The concave portion and the convex portion are engaged all around. With this connection structure, the internal gear 38 and the brake drum can be positioned substantially coaxially, and can be integrally rotated with the relative rotational displacement being restricted.

In the involute serration, a pair of convex portions and concave portions constituting the serration are formed by teeth having a tooth shape including an involute curve. For example, the aforementioned teeth 38a and teeth 29a have an involute tooth profile and have the same number, modules, and pressure angle (eg, 45 degrees) as each other. This tooth profile can be obtained by processing easily and with high precision in the same manner as the gear teeth of a normal gear.

The brake drum is an annular portion composed of the large diameter portion 29 of the upper gear case 30 described above. The brake drum is formed of a metal material and has wear resistance. On the inner peripheral surface of the large-diameter portion 29, a large number of the above-mentioned teeth 29a constituting the involute serration are formed. These teeth 29a extend in the axial direction, and are formed in a waveform that is regularly continuous over the entire circumference of the inner peripheral surface.

Here, the teeth 29a are
The size of the teeth 29a is set so that the deformation of the brake drum becomes substantially uniform as a whole due to the tightening of the brake drum and the load from the internal gear 38, and the contact with the brake shoe 49 can be properly maintained. Have been. For example, the outer diameter of the brake drum is 90 mm, the inner diameter is 80.55 mm, the height of the teeth 29a is 1.5 mm, and the number of teeth is 108.

In the brake drum, the contact surface with which the brake shoe 49 comes into contact is set on a part of the outer peripheral surface of the large diameter portion 29, and the contact surface and the teeth 29a are located at substantially the same position in the axial direction. Are located. The internal gear 38 is formed of a resin material in a cylindrical shape, a plurality of gear teeth 38b for forming a gear are formed on the inner peripheral surface, and a plurality of teeth 38a forming an involute serration are formed on the outer peripheral surface. Have been. The teeth 38a extend in the axial direction, and are formed in a waveform that is regularly continuous over the entire circumference of the outer peripheral surface. For example, the number and size of the teeth 38a are set so as to satisfy the strength required for transmitting the torque of the motor 13. The teeth 38a are located in a part of the internal gear 38 in the axial direction, and are arranged at substantially the same axial positions as the gear teeth 38b.

According to this connection structure, the internal gear 38 and the brake drum are connected so as to be integrally rotatable. Stirring blade 1
When only 1 is driven, the internal gear 38 is stopped by the brake mechanism 27, and the internal gear 38 receives a load (reaction force) in the direction of rotation from the planetary gear 39. This load is received by the brake shoe 49 via the connection structure and the brake drum.

At this time, the brake drum receives the tightening force from the brake shoe 49 and the load from the internal gear 38. However, as described later, the load is dispersed to make the brake drum uneven. Deformation is prevented. As a result, shape accuracy such as roundness of the outer peripheral surface of the brake drum can be maintained, and distortion of the circular cross section of the brake drum can be prevented. Therefore, the brake shoe 49 wound around the outer peripheral surface of the brake drum can be prevented from hitting the contact surface of the brake drum in one side, so that the contact surface can be surely contacted and the brake noise can be prevented.

At this time, since the deformation of the internal gear 38 due to the load received from the planetary gear 39 is also suppressed as described later, the meshing between the internal gear 38 and the planetary gear 39 can be properly maintained. Gear noise can be prevented. In addition, since the plurality of irregularities on the entire circumference are fitted by the serration engagement, the connection can be surely made without rattling. Further, even in the case where an overload is applied, the load can be distributed over the entire circumference, so that rattling hardly occurs. As a result, noise due to rattling can be prevented.

Further, since the internal gear 38 and the brake drum can be connected with high concentricity by the serration engagement, the assembling accuracy of the gear mechanism 25 can be increased, and the gear noise of the internal gear 38 can be reduced. be able to. As described above, according to the present embodiment, the inner peripheral surface of the brake drum is formed in a regular waveform over the entire circumference by the serration. As a result of preventing the deformation from becoming non-uniform, the shape accuracy of the brake drum can be maintained. Therefore, the above-described brake noise can be prevented. In the case of the related art in which the key grooves are dispersedly arranged at four locations on the inner periphery of the brake drum, the brake drum is likely to be deformed unevenly such that the circular cross section of the brake drum becomes quadrangular. This may occur.

Further, since the brake drum is engaged with and connected to the entire circumference of the internal gear 38 by serrations, the load applied to the brake drum from the internal gear 38 can be dispersed and received over the entire circumference. The shape accuracy of the brake drum can be more reliably maintained. Therefore, brake noise can be reliably prevented. Further, in the brake drum, the teeth 29a and the contact surface are disposed at substantially the same position in the axial direction, so that the brake shoe 4 during the braking operation is provided.
9 can be supported by the internal gear 38, so that deformation of the brake drum can be easily suppressed, and as a result, brake noise can be more reliably prevented.

Further, since the internal gear 38 is connected by serrations that engage with the entire circumference, the load applied to the internal gear 38 can be uniformly received over the entire circumference.
8 can be prevented. Therefore, the meshing between the internal gear 38 and the planetary gear 39 can be properly maintained, and gear noise can be prevented. In particular, the internal gear 38 is connected to the brake drum on its outer peripheral surface, and the teeth 38a and the gear teeth 38b of the internal gear 38 are located at substantially the same position in the axial direction. Since the torsional deformation of the internal gear 38 can be suppressed, the above-described gear noise can be reliably prevented.

Since the internal gear 38 is made of resin, gear noise can be further reduced when the internal gear 38 meshes with the planetary gear 39. In addition, since the serration is an involute serration, high-precision machining is easy, and high-precision connection can be realized. Therefore, the load applied to the internal gear 38 and the brake drum can be uniformly and reliably distributed over the entire circumference. Therefore, the partial applied force can be reduced, and the deformation of the internal gear 38 and the brake drum as a whole can be reliably prevented from becoming uneven. As a result, gear noise and brake noise can be reliably prevented.

In the case of a brake drum having serrations all around the inner peripheral surface, uneven deformation of the brake drum can be prevented, so that the brake drum can be made thinner, and as a result, it can be manufactured at low cost. Can be. In particular,
In the involute serration, the load applied to the brake drum can be reliably dispersed and reduced over the entire circumference, so that the thickness of the brake drum can be reliably reduced, so that the brake drum can be manufactured at lower cost. For example, it is conceivable to manufacture a brake drum by molding a sheet metal material. Moreover, involute serration is easy to process.

In the above embodiment, the connection structure is described as involute serration.
It is not limited to this. For example, a triangular serration can be considered. In short, it is only necessary that there be a pair of serrations that can be engaged with each other. In the above-described embodiment, the serrations are formed on the inner periphery of the brake drum.
It may be provided on a portion of the outer shaft other than the brake drum.

In addition, various design changes can be made without departing from the scope of the present invention.

[0041]

According to the first aspect of the present invention, since the load on the internal gear can be dispersed by the serration engagement, deformation of the internal gear is prevented, and gear noise when the internal gear meshes is reduced. can do. Further, since the outer shaft engaged with the internal gear by serration can be prevented from being deformed unevenly, the outer shaft can be made thinner and manufactured at low cost.

According to the invention described in claim 2, according to claim 1
In addition to the effects of the present invention, the following effects can be obtained. In other words, by using involute serration, deformation of the internal gear and the outer shaft can be reliably prevented by high-precision machining, so that gear noise can be reliably prevented. Moreover, in addition to being easy to process, the outer shaft can be reliably thinned by high precision processing and reduction of load. Can be manufactured.

According to the invention described in claim 3, according to claim 1
In addition to the effects of the invention according to the second aspect, the internal gear made of resin can further reduce gear noise when meshing with the planetary gear. According to the invention described in claim 4,
In addition to the effects of the invention according to any one of claims 1 to 3,
In the outer shaft serrated and engaged with the internal gear, the deformation of the outer shaft can be prevented from becoming uneven, so that the brake noise when the brake member winds around the outer peripheral surface of the outer shaft can be prevented. In particular, in the case of involute serration, uneven deformation of the outer shaft can be reliably prevented, and brake noise can be reliably prevented.

[0044]

[Brief description of the drawings]

FIG. 1 is a side sectional view of a schematic configuration of a washing machine having a washing machine speed reduction mechanism according to an embodiment of the present invention.

FIG. 2 is a partially sectional front view of a bearing of the washing machine of FIG. 1;

FIG. 3 is a partial cross-sectional bottom view of a bearing portion of the washing machine of FIG. 1;

FIG. 4 is an exploded perspective view of a main part of a bearing of the washing machine of FIG. 1;

FIG. 5 is an enlarged sectional view of a main part of FIG. 3;

[Explanation of symbols]

 Reference Signs List 3 inner tub (dehydration tub) 11 stirring blade 16 bearing unit (reducing mechanism for washing machine) 21 inner shaft 29 large diameter portion (outer shaft) 29a tooth (serration) 38 internal gear 38a tooth (serration) 38b gear tooth 39 planetary gear 49 Brake shoe (brake member)

──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int.Cl. ⁷ , DB name) D06F 37/30-37/40

Claims (4)

(57) [Claims] An inner shaft connected to a dehydration tub and integrally rotating; an inner shaft connected to a stirring blade and integrally rotated; a ring-shaped internal gear mounted on the outer shaft; and, in a washing machine and a gear mechanism having a planetary gear coupled to the inner shaft and, the internal gear is formed in the outer shaft separately from, have a gear tooth of the planetary gear and meshed with the inner peripheral surface thereof In addition, the outer peripheral surface has serrations, and the inner peripheral surface of the outer shaft has serrations that engage with the outer peripheral surface of the internal gear so that slip does not occur with respect to the outer peripheral surface of the internal gear.
The internal gear has an external shaft so that the load on the internal gear can be distributed.
A washing machine characterized in that a serration is engaged with the washing machine . 2. The method of claim 1, wherein the washing machine, the serrations of the outer shaft and the inner gear, a washing machine, which is a involute serration. 3. An apparatus according to claim 1 or 2, wherein the washing machine, the internal gear, a washing machine, characterized in that it is formed of a resin. 4. A brake member wound around an outer peripheral surface of an outer shaft to stop rotation of a dehydration tub during washing and rinsing, in the washing machine according to claim 1. A washing machine characterized by being provided with.