WO2015161580A1

WO2015161580A1 - Rotary drum washing machine

Info

Publication number: WO2015161580A1
Application number: PCT/CN2014/083633
Authority: WO
Inventors: 田中启之; 竹中卓雄
Original assignee: 海尔亚洲国际株式会社; 青岛海尔洗衣机有限公司
Priority date: 2014-04-25
Filing date: 2014-08-04
Publication date: 2015-10-29
Also published as: JP6397216B2; CN105264138A; JP2015208500A; CN105264138B

Abstract

Disclosed is a rotary drum washing machine, wherein a drive part (30) comprises a rotary drum shaft (300), a flank shaft (200), a variable speed mechanism (400) and a bearing unit (500). The bearing unit (500) has a first roller bearing (513) and a second roller bearing (523) configured in such a way as to sandwich the variable speed mechanism (400). The rotary drum shaft (300) comprises a front shaft part (300a) supported by the first roller bearing (513), a rear shaft part (300b) supported by the second roller bearing (523), and a housing part (300c) expanding further outwards than the front shaft part (300a) and the rear shaft part (300b) and housing the variable speed mechanism (400). The bearing unit (500) contains a front unit (510) comprising the first roller bearing (513) and a rear unit (520) comprising the second roller bearing (523), the front unit (510) and the rear unit (520) joining from the two sides of the housing part (300c) in the axial direction of the rotary drum shaft (300), and thereby being able to prevent an increase in the size of the drive part, ensuring washing capacity, and allowing better consistency for the central precision of the two bearings, realizing improved cleaning performance.

Description

Technical field

The present invention relates to a drum washing machine.

It is also possible to wash but not to dry. Background technique

Conventionally, the drum washing machine rotates the drum of the horizontal axis type in the outer tank in which the water is stored in the bottom, lifts and lowers the laundry by a baffle provided in the drum, and passes the laundry to the inner peripheral surface of the drum. The laundry is washed by being beaten (refer to Patent Document 1).

Thus, in the structure in which the laundry is stirred by the baffle, the laundry is hardly entangled with each other or the mechanical force acting on the laundry is liable to be smaller than that of the fully automatic washing machine, and the washing performance is easily lowered.

Therefore, in the drum washing machine, in order to improve the washing performance, it is possible to provide a structure in which a stirring body is provided on the rear surface of the drum, and the drum and the stirring body are rotated at different rotation speeds during washing or rinsing.

Prior art literature

Patent literature

Patent Document 1: Japanese Laid-Open Patent Publication No. 2013-240577 SUMMARY OF INVENTION

Problems to be solved by the invention

When the drum washing machine that rotates the drum and the agitating body at different rotational speeds is realized, the driving unit of the driving drum and the agitating body is increased in size by adding a speed reducing mechanism or the like, thereby making it easy to increase the size. Therefore, in order to suppress the reduction in the size of the outer tub and the drum and to ensure the washing capacity as much as possible, it is necessary to suppress an increase in the size of the driving portion.

The present invention has been made in view of the above problems, and an object thereof is to provide a drum washing machine capable of achieving an improvement in cleaning performance while suppressing an increase in size of a driving portion.

Solution to solve the problem

A drum washing machine according to a main aspect of the present invention includes: an outer tank disposed in a casing; and a drum disposed in the outer tank and rotatable about a horizontal axis or an inclined axis inclined with respect to a horizontal direction; a baffle disposed on an inner circumferential surface of the drum; a rotating body disposed at a rear portion of the drum, having a protrusion on the surface in contact with the laundry; and a driving portion to rotate the rotating body The drum and the rotating body are rotated in a manner faster than the rotational speed of the drum. Here, the driving unit includes a driving motor; the first rotating shaft is coupled to the rotating body, and transmits torque of the driving motor to the rotating body; and a shifting mechanism that shifts a rotation of a rotor of the driving motor a second rotating shaft coupled to the drum, transmitting torque of the driving motor to the drum, and enclosing the first rotating shaft and the speed reducing mechanism; and a bearing unit having a shifting force therebetween The first bearing and the second bearing disposed in a manner of the mechanism support the second rotating shaft in a rotatable manner by the first bearing and the second bearing. Further, the second rotating shaft includes: a first shaft portion supported by the first bearing; a second shaft portion supported by the second bearing; and a receiving portion toward the first shaft portion and the The outer side of the second shaft portion bulges and accommodates the shifting mechanism. Further, the bearing unit includes a first unit including the first bearing and a second unit including the second bearing, the first unit and the second unit being in an axial direction of the second rotating shaft Both sides of the receiving portion are combined.

According to the above configuration, since the space generated between the first bearing and the second bearing is utilized as the arrangement space of the speed reduction mechanism, the load generated by the drum is well supported by the second rotating shaft, and therefore the axis of the second rotating shaft can be The direction reduces the size of the drive portion. Thereby, the outer tub and the drum can be made larger in the front-rear direction, so that the washing capacity can be increased.

Further, according to the above configuration, since the second rotating shaft of the inner package shifting mechanism can be housed inside the bearing unit by combining the first unit and the second unit, it is not necessary to use the opening for inserting the second rotating shaft. The first bearing and the second bearing, which are large in shape, are required to be larger than the thickness of the first shaft portion and the second shaft portion as necessary.

In the drum washing machine of the present aspect, a structure may be employed in which the first unit has a first circumferential surface having a circular or circular arc shape concentric with the first bearing, and The second unit has a second circumferential surface having a circular or circular arc shape concentric with the second bearing. In this case, the first unit and the second unit are coupled by the insertion and fitting of the first circumferential surface and the second circumferential surface.

According to the above configuration, even in the case of a structure in which the bearing unit is divided, the center of the first bearing and the center accuracy of the second bearing can be satisfactorily matched. Therefore, it is possible to prevent the second rotating shaft from being smoothly rotated due to the misalignment of the center of the first bearing and the axis of the second bearing.

In the drum washing machine of the present aspect, the following structure may be employed, that is, the first portion of the bearing unit The two units are located on the side of the drive motor, and the second unit is provided with a fixing portion for fixing the stator of the motor.

According to the above configuration, since the stator is fixed to the second unit provided with the second bearing, the center of the rotor concentric with the second bearing can be satisfactorily matched with the center accuracy of the stator. Thereby, since the gap between the rotor and the stator can be kept constant, it is possible to stably drive the motor and rotate it.

In the drum washing machine of the present aspect, the shifting mechanism can be configured to include a speed reduction mechanism that decelerates the rotation of the rotor. In this case, the speed reduction mechanism has: a sun gear that rotates with rotation of a rotor of the drive motor; an annular internal gear that surrounds the sun gear; and a plurality of planet gears interposed between the sun gear And the internal gear; and the planetary carrier, the planetary gears are rotatably held. The second rotating shaft is fixed to the internal gear, and rotates accompanying the rotation of the internal gear. Further, the planetary carrier includes a shaft portion coaxial with the second rotation shaft and a front end portion protruding from the rotor side from the second rotation axis. The drive portion also includes a clutch mechanism portion. The clutch mechanism portion is configured to switch the shape of the driving portion between the first form and the second form in relation to a front end portion of the shaft portion protruding from the second rotating shaft, wherein the first portion In a state in which the shaft portion is in a non-rotatable state, the first rotating shaft and the second rotating shaft are rotated so that the first degree is slow, and the second form is The shaft portion is rotated together with the rotor, and the first rotating shaft, the speed reducing mechanism, and the second rotating shaft are integrally rotated at a rotation speed equal to a rotation speed of the rotor.

According to the above configuration, the second rotating shaft is coupled to the internal gear, and the front end portion of the shaft portion provided on the planetary carrier protrudes toward the outer surface of the second rotating shaft, and the clutch mechanism portion is associated with the protruding front end portion. Thereby, the operation of the speed reduction mechanism is switched, and the form of the drive unit is switched between the first form and the second form. Thereby, as a result of the configuration in which the speed reduction mechanism is sandwiched between the first bearing and the second bearing, even if the speed reduction mechanism is housed in the second rotating shaft, the first form and the second form can be satisfactorily performed. Switch between forms. Further, by adjusting the number of teeth of the sun gear and the internal gear, the reduction ratio of the rotor and the second rotating shaft can be set, and a wide reduction ratio can be set.

In the case of the above-described configuration, the clutch mechanism portion may include a clutch body that is fitted into the distal end portion and that is axially oriented with respect to the distal end portion of the shaft portion. The movement is allowed and the rotation to the circumferential direction of the shaft portion is restricted; and the movement mechanism portion is made to The clutch body moves in the direction of the axis. In this case, a first "" joint portion and a second engagement portion are respectively provided at an end portion of the clutch body on the bearing unit side and an end portion on the rotor side. Further, the second unit located on the side of the drive motor is provided with a first engaged portion, and the rotor is provided with a second engaged portion. The clutch body is opposite to the second when the clutch body is moved to the second unit side by the moving mechanism portion and the first engaging portion is engaged with the first engaged portion The rotation of the unit in the circumferential direction is restricted, the shaft portion is in a state of being non-rotatable, and the clutch body is moved to the rotor side by the moving mechanism portion and the second engaging portion and the second portion are When the engaged portion is engaged, the rotation of the clutch body with respect to the rotor in the circumferential direction is restricted, and the shaft portion is rotatable together with the rotor.

According to this configuration, the clutch mechanism portion that switches between the first form and the second form by the form of the drive portion can be specifically realized by the planetary carrier. Further, since the first engaged portion that engages with the first engaging portion of the clutch body is formed in the second unit in which the second bearing is disposed concentrically with the shaft portion of the clutch body, the center of the first engaging portion The center of the first engaged portion can be accurately engaged.

In the case of the above configuration, the moving mechanism portion may include an elastic member interposed between the clutch body and the bearing unit to cause the clutch body to pass the elastic force. Moving to the rotor side to engage the second engaging portion with the second engaged portion; and pressing member to press the clutch body to the bearing unit Moving laterally, and contacting the clutch body in a state in which the first engaging portion is engaged with the first engaged portion, in the second engaging portion and the second engaged portion In the engaged state, it is separated from the clutch body.

According to this configuration, the clutch body is moved by the elastic force of the elastic member, whereby the second engagement portion is engaged with the second engaged portion, and when the clutch body and the rotor are rotated together by the engagement, The pressing member is in a state of being separated from the clutch body. Therefore, the rotation of the rotor and the clutch body is not hindered by the contact of the pressing member with the clutch body.

Effect of the invention

According to the present invention, it is possible to provide a drum washing machine which can improve the cleaning performance while suppressing an increase in the size of the driving portion.

The effects and significance of the present invention will be further clarified by the description of the embodiments described below. However, the following embodiments are merely illustrative of the embodiments of the present invention, and the present invention is not limited by the following description. DRAWINGS

Fig. 1 is a side cross-sectional view showing the structure of a drum washing machine according to an embodiment.

Fig. 2 is a cross-sectional view showing the configuration of a drive unit of the embodiment.

Fig. 3 is a front elevational view showing the rotor of the drive motor of the embodiment.

4 is a view showing a configuration of a wing shaft, a drum shaft, and a planetary gear mechanism according to an embodiment.

Fig. 5 is a view showing a configuration of a front unit of a bearing unit according to an embodiment;

Fig. 6 is a view showing a configuration of a rear unit of a bearing unit according to an embodiment;

Fig. 7 is a view showing a structure of a rear unit of a bearing unit according to an embodiment.

8 is a view showing a configuration of a clutch body of a clutch mechanism portion according to an embodiment.

Fig. 9 is a view showing a configuration of a moving mechanism portion of a clutch mechanism portion according to an embodiment.

Fig. 10 is a view for explaining an operation of a clutch mechanism unit of the embodiment.

Fig. 11 is a view for explaining the operation of the drive unit, the drum, and the agitating body in the washing step and the rinsing step of the embodiment.

Fig. 12 is a view for explaining the operation of the drive unit, the drum, and the agitating body in the intermediate dehydration program and the final dehydration program in the embodiment.

Fig. 13 is a view showing the configuration of a drive unit which is compared with the embodiment. detailed description

Hereinafter, a drum washing machine which does not have a drying function as an embodiment of the drum washing machine of the present invention will be described with reference to the drawings.

Fig. 1 is a side cross-sectional view showing the structure of a drum washing machine 1.

The drum washing machine 1 has a casing 10 constituting an outer appearance. The front surface 10a of the casing 10 is inclined upward from the central portion, and an input port 11 for washing is formed on the inclined surface. The inlet 11 is covered by a door 12 that is opened and closed.

In the casing 10, the outer groove 20 is elastically supported by a plurality of dampers 21. The drum 22 is rotatably disposed in the outer tub 20. The outer groove 20 and the rear surface side of the drum 22 are inclined so as to be lowered in the horizontal direction. Thereby, the drum 22 rotates centering on the inclination axis inclined with respect to the horizontal direction. The inclination angle of the outer tub 20 and the drum 22 can be made to be about 10 to 20 degrees. The opening 20a of the front surface of the outer tub 20 and the opening 22a of the front surface of the drum 22 face the input port 11 and pass through the input port 11 The door 12 is closed. On the inner peripheral surface of the drum 22, a plurality of dewatering holes 22b are formed. Further, the three baffles 23 are provided on the inner circumferential surface of the drum 22 at substantially equal intervals in the circumferential direction.

The agitating body 24 is rotatably disposed at the rear of the drum 22. The agitating body 24 has a substantially disk shape. A plurality of blades 24a extending radially from the center portion are formed on the surface of the agitating body 24. The agitating body 24 rotates coaxially with the drum 22. The agitating body 24 corresponds to the rotating body of the present invention, and the vane 24a corresponds to the projecting portion of the present invention.

A drive unit 30 that generates torque for driving the drum 22 and the agitating body 24 is disposed behind the outer tub 20. The drive unit 30 corresponds to the drive unit of the present invention. The drive unit 30 rotates the drum 22 and the agitating body 24 at different rotational speeds in the same direction during the washing process and the rinsing process. Specifically, the drive unit 30 rotates the drum 22 at a rotational speed at which the centrifugal force applied to the laundry in the drum 22 is less than the gravity, so that the agitating body 24 rotates at a rotational speed faster than the rotational speed of the drum 22. On the other hand, the driving unit 30 integrally rotates the drum 22 and the agitating body 24 at a rotational speed at which the centrifugal force of the laundry applied to the drum 22 is much larger than the gravity during the spin-drying process. The detailed structure of the drive unit 30 will be described later.

A drain port portion 20b is formed at the bottom of the outer tub 20. A drain valve 40 is provided in the drain port portion 20b. The drain valve 40 is connected to the drain pipe 41. When the drain valve 40 is opened, the water stored in the outer tank 20 is discharged to the outside through the drain pipe 41.

A detergent box 50 is disposed in the front upper portion of the casing 10. The lotion container 50a containing the detergent in the detergent box 50 is housed so as to be freely detachable from the front. The detergent box 50 is connected to the water supply valve 51 disposed at the rear upper portion in the casing 10 through the water supply pipe 52. Further, the detergent box 50 is connected to the upper portion of the outer tub 20 through a water injection pipe 53. When the water supply valve 51 is opened, tap water is supplied from the faucet to the outer tank 20 through the water supply pipe 52, the detergent box 50, and the water injection pipe 53. At this time, the detergent contained in the lotion container 50a is supplied to the outer tub 20 along the water flow.

Next, the structure of the drive unit 30 will be described in detail.

FIG. 2 is a cross-sectional view showing the structure of the drive unit 30. FIG. 3 is a front view showing the rotor 110 of the structure of the rotor 110 of the drive motor 100. 4(a) and (b) are views showing the configurations of the wing shaft 200, the drum shaft 300, and the planetary gear mechanism 400. Figure 4 (a) is a side cross-sectional view, and Figure 4 (b) is a cross-sectional view taken along line A-A' of Figure 4 (a). 5(a) and (b) are views showing the structure of the front unit 510 of the bearing unit 500, which are a front view and a rear view, respectively, of the front unit 510. 6 and 7 are views showing the configuration of the rear unit 520 of the bearing unit 500. FIG. 6 is a front view of the rear unit 520. 7(a) is a rear view of the rear unit 520, and FIG. 7(b) is an enlarged perspective view of the rear portion of the rear unit 520. 8(a) to (c) are diagrams showing the configuration of the clutch body 610 of the clutch mechanism portion 600, which are a front view, a right side view, and a rear view, respectively, of the clutch body 610. 9(a) to 9(c) are diagrams showing the configuration of the movement mechanism portion DM of the clutch mechanism portion 600, and are a rear view, a right side view, and a plan view, respectively, of the movement mechanism portion DM. 10(a) and (b) are diagrams for explaining the operation of the clutch mechanism unit 600. Further, in FIGS. 8(a) to (c), the state in which the clutch body 610 has been mounted on the carrier shaft 442 of the carrier 440 is shown.

The drive unit 30 includes a drive motor 100, a wing shaft 200, a drum shaft 300, a planetary gear mechanism 400, a bearing unit 500, and a clutch mechanism portion 600. The drive motor 100 generates torque for driving the agitating body 24 and the drum 22. The wing shaft 200 is rotated by the torque of the drive motor 100, and the rotation is transmitted to the agitating body 24. The wing shaft 200 corresponds to the first rotating shaft of the present invention. The planetary gear mechanism 400 decelerates the rotation of the wing shaft 200, i.e., the rotation of the rotor 110 of the drive motor 100, and transmits it to the drum shaft 300. The planetary gear mechanism 400 corresponds to the shifting mechanism and the speed reducing mechanism of the present invention. The drum shaft 300 rotates coaxially with the wing shaft 200 at a rotational speed decelerated by the planetary gear mechanism 400, and transmits the rotation to the drum 22. The drum shaft 300 corresponds to the second rotating shaft of the present invention. The bearing unit 500 is capable of supporting the wing shaft 200 and the drum shaft 300 in a rotatable manner. The clutch mechanism unit 600 switches between the first mode and the second mode in which the configuration of the driving unit 30 is such that the agitating body 24, that is, the wing shaft 200, is equal to the rotational speed of the driving motor 100. The rotation speed is rotated to rotate the drum 22, that is, the drum shaft 300, at a rotation speed decelerated by the planetary gear mechanism 400. In the second aspect, the agitating body 24 and the drum 22, that is, the wing shaft 200, the drum shaft 300, and the planetary gear mechanism can be rotated. The 400 rotates integrally at a rotation speed equal to that of the drive motor 100.

Referring to Fig. 2 and Fig. 3, the drive motor 100 is an outer rotor type DC brushless motor, and includes a rotor 110 and a stator 120. The rotor 110 is formed in a bottomed cylindrical shape, and the permanent magnets 111 are arranged over the entire circumference on the inner peripheral surface thereof. As shown in Fig. 3, a circular boss portion 112 is formed at a central portion of the rotor 110. A boss hole 113 for fixing the wing shaft 200 is formed in the boss portion 112, and an annular engaged recess 114 is formed on the outer circumference of the boss hole 113. The outer peripheral portion of the engaged concave portion 114 has the uneven portion 114a over the entire circumference. The engaged recess 114 corresponds to the second engaged portion of the present invention.

The stator 120 has a coil 121 at the outer peripheral portion. When a control circuit, not shown, supplies a drive current to the coil 121 of the stator 120, the rotor 110 rotates. A screw hole 122 is formed at an upper portion of the stator 120 and at three left and right intervals at intervals of approximately 120 degrees. Each of the screw holes 122 has a phase from the center of the stator 120 to the radial direction Same distance. Further, in Fig. 2, only one screw hole 122 above is illustrated.

Referring to Figures 2 and 4, the drum shaft 300 has a hollow shape and encloses a wing shaft 200 and a planetary gear mechanism 400. The drum shaft 300 includes a front shaft portion 300a, a rear shaft portion 300b, and a housing portion 300c provided between the front shaft portion 300a and the rear shaft portion 300b and bulging outward from the front shaft portion 300a and the rear shaft portion 300b. The shaft portion 300a corresponds to the first shaft portion of the present invention, and the rear shaft portion 300b corresponds to the second shaft portion of the present invention.

The planetary gear mechanism 400 is housed in the accommodating portion 300c. The front portion of the front shaft portion 300a is formed to be larger than the inner diameter of the rear portion, and the first sliding bearing 301 is disposed in the large diameter portion 300d having a large inner diameter. Similarly, a mechanical seal 302 is disposed in front of the first sliding bearing 301 with a restriction ring to be described later interposed therebetween in the large diameter portion 300d. The first sliding bearing 301 and the mechanical seal 302 are inserted into the large diameter portion 300d from the front side, and are fixed to the drum shaft 300 by press fitting or the like. Further, the drum shaft 300 is divided in the front-rear direction, and is composed of two members, that is, the front member M1 and the rear member M2, so that the planetary gear mechanism 400 can be housed in the accommodating portion 300c.

The planetary gear mechanism 400 includes: a sun gear 410; an annular inner gear 420 surrounding the sun gear 410; a plurality of sets of planet gears 430 interposed between the sun gear 410 and the internal gear 420; and being rotatably held by the support shaft 441 Planetary carrier 440 of these planet gears 430.

A set of planet gears 430 has a first gear 431 and a second gear 432. The two gears of the first gear 431 and the second gear 432 mesh with each other, and the first gear 431 meshes with the sun gear 410, and the second gear 432 meshes with the internal gear 420. The planet carrier 440 includes a carrier shaft 442 that extends rearward. The carrier shaft 442 corresponds to the shaft portion of the present invention. The carrier shaft 442 is coaxial with the drum shaft 300, and the inner portion is formed to be hollow to allow the wing shaft 200 to be inserted. The carrier shaft 442 is formed to have a larger inner diameter than the root portion from the front end portion to the root portion, and the second sliding bearing 443 is disposed on the large diameter portion 442a having a large inner diameter. A rack 442c is formed on the outer peripheral surface of the front end portion 442b of the carrier shaft 442 that protrudes rearward from the drum shaft 300.

An annular restricting flange 201 is formed at a rear end portion of the wing shaft 200. The wing shaft 200 is inserted into the drum shaft 300 from the rear. An annular restriction ring 202 is fixed to the front end portion of the inserted wing shaft 200. Similarly to the first sliding bearing 301 and the mechanical seal 302, the restriction ring 202 is inserted into the large diameter portion 300d from the front side, and is fixed to the wing shaft 200 by a fixing method such as press fitting. The confinement ring 202 is in contact with the first sliding bearing 301 via the first washer 203 and is in contact with the mechanical seal 302 via the second washer 204. The restricting flange 201 is engaged with the rear end of the carrier shaft 442, and is engaged with the first sliding bearing 301 via the first washer 203 through the restricting ring 202, This restricts the movement of the wing shaft 200 in the forward and backward directions.

The wing shaft 200 inserted into the inside of the drum shaft 300 has its outer peripheral surface sliding between the first sliding bearing 301 and the second sliding bearing 443. Thereby, the wing shaft 200 smoothly rotates in the drum shaft 300. Further, water can be prevented from intruding between the drum shaft 300 and the wing shaft 200 by the mechanical seal 302. Further, when the wing shaft 200 rotates, the restriction ring 202 slides between the first washer 203 and the second washer 204. Therefore, the abrasion of the first sliding bearing 301 and the mechanical seal 302 caused by the sliding of the restriction ring 202 can be prevented.

Further, as described above, since the first slide shaft 301, the restriction ring 202, and the mechanical seal 302 can all be inserted into the large-diameter portion 300d by being inserted from the front, the assemblability can be improved.

A sun gear 410 is fixed to an intermediate portion of the wing shaft 200. As shown in FIG. 4(b), a key portion 421 extending in the front-rear direction is formed at a plurality of positions on the outer circumferential surface of the internal gear 420, and a key groove portion 303 corresponding to the key portion 421 is formed on the inner circumferential surface of the drum shaft 300. . The key shaft 421 is engaged with the key groove portion 303, and the roller shaft 300 and the internal gear 420 are fixed in the circumferential direction. Further, the rear end portion of the wing shaft 200 projects rearward from the carrier shaft 442 and is fixed to the boss hole 113 of the rotor 110.

When the wing shaft 200 rotates with the rotation of the rotor 110, the sun gear 410 rotates. When the planetary carrier 440 is in a state of being fixed in a non-rotational manner, since the planetary gear 430 cannot revolve, only the rotation of the sun gear 410 is performed with the rotation. That is, the first gear 431 rotates in the opposite direction to the sun gear 410, and the second gear 432 rotates in the same direction as the sun gear 410. With the rotation of the second gear 432, the internal gear 420 is in the same direction as the second gear 432, i.e., rotates in the same direction as the sun gear 410. Thereby, the drum shaft 300 fixed to the internal gear 420 is rotated. Further, the directions of rotation of the respective gears 410, 420, 431, 432 and the drum shaft 300 are indicated by arrows in Fig. 4 (b). Rotate at a lower rotational speed than the wing shaft 200. Thus, since the rotational speed of the wing shaft 200 is decelerated and transmitted to the drum shaft 300, the torque transmitted to the drum shaft 300 becomes larger than the torque transmitted from the drive motor 100 to the wing shaft 200.

Referring to Figures 2, 5, 6, and 7, the bearing unit 500 includes a front unit 510 and a rear unit 520. The front unit 510 and the rear unit 520 correspond to the first unit and the second unit of the present invention, respectively.

A cylindrical front bearing portion 511 is provided at a central portion of the front unit 510. A mechanical seal 512 is disposed on the front side of the front bearing portion 511, and a first rolling bearing 513 is disposed on the rear side. The first rolling bearing 513 corresponds to the first bearing of the present invention. Formed around the front bearing portion 511 on the rear side of the front unit 510 There is a fitting recess 514. The outer peripheral surface 514a of the fitted recessed portion 514 has a circular shape whose center coincides with the center P1 of the first rolling bearing 513 disposed in the state of the front bearing portion 511. The outer peripheral surface 514a of the fitted recessed portion 514 corresponds to the first circumferential surface of the present invention.

Mounting holes 515 are formed in the outer peripheral portion of the front unit 510 at four positions of up, down, left, and right. Further, two mounting bosses 516 are formed at the lower portion of the outer peripheral portion of the front unit 510. Mounting holes 516a are formed in the mounting boss 516.

A cylindrical covering portion 521 having an inner diameter slightly larger than the outer diameter of the accommodating portion 300c of the drum shaft 300 and covering the accommodating portion 300c is provided on the rear side of the central portion of the rear unit 520, behind the covering portion 521. A cylindrical rear bearing portion 522 having an inner diameter smaller than the outer diameter of the accommodating portion 300c is provided. In front of the rear bearing portion 522 of the second rolling bearing 523 is disposed, the impact plate ₅₂₄ is provided with a spring behind the second rolling bearing 523. The second rolling bearing 523 corresponds to the second bearing of the present invention. A rack 525 is formed on the inner surface of the rear end portion of the rear bearing portion 522 over the entire circumference. The rack 525 corresponds to the first engaged portion of the present invention.

Three mounting bosses 526 are formed on the rear side of the rear unit 520. Each of the mounting bosses 526 is formed at three positions above and to the left and right corresponding to the screw holes 122 of the stator 120, respectively. Mounting holes 526a are formed in the mounting boss 526. Each of the mounting holes 526a has a distance from the center P2 of the second rolling bearing 523 disposed in the state of the rear shaft portion 522 to the same radial direction. The mounting boss 526 corresponds to the fixing portion of the present invention.

An annular fitting rib 527 is formed on the front side of the central portion of the rear unit 520. The outer peripheral surface 527a of the fitting rib 527 has a circular shape whose center coincides with the center P2 of the second rolling bearing 523. The diameter of the outer peripheral surface 527a of the fitting rib 527 is equal to the diameter of the outer peripheral surface 514a of the fitted recess 514. The outer peripheral surface 527a of the fitting rib 527 corresponds to the second circumferential surface of the present invention.

A screw hole 528 is formed in the outer peripheral portion of the rear unit 520. Each of the screw holes 528 is formed at four positions of up, down, left, and right corresponding to the mounting holes 515 of the front unit 510.

The front unit 510 is coupled to the rear unit 520 in a state where the inner wrap shaft 200 and the drum shaft 300 of the planetary gear mechanism 400 are set to the front unit 510. At this time, the fitting rib 527 is fitted into the fitted recess 514. In the fitted state, the outer peripheral surface 527a of the fitting rib 527 is in contact with the outer peripheral surface 514a of the fitted recess 514. Thus, the front unit 510 and the rear unit 520 are joined by the insertion and fitting of the outer circumferential surface 527a of the fitting rib 527 and the outer circumferential surface 514a of the fitting recess 514. The screw 530 is blocked by the mounting hole 515 through the screw hole 528. Thereby, the front unit 510 and the rear unit 520 are fixed. Thus, the drum shaft 300 is disposed inside the bearing unit 500. The planetary gear mechanism 400 is housed in the accommodating portion 300c of the drum shaft 300, and is disposed in a space generated between the first rolling bearing 513 and the second rolling bearing 523. Here, it is necessary to provide a certain distance between the first rolling bearing 513 and the second rolling bearing 523 of the bearing unit 500 so that the load generated by the heavy drum 22 is well supported by the drum shaft 300. In the present embodiment, since the space generated between the first rolling bearing 513 and the second rolling bearing 523 is used as the arrangement space of the planetary gear mechanism 400, the configuration of the planetary gear mechanism 400 is disposed behind the two rolling bearings 513 and 523. The size of the drive unit 30 in the axial direction of the drum shaft 300 can be reduced.

The outer peripheral surface of the front shaft portion 300a of the drum shaft 300 is joined by the first rolling shaft 7 513 7 and the rear shaft portion 300b is received by the second rolling bearing 523. Thereby, the drum shaft 300 smoothly rotates in the bearing unit 500. Further, by providing the mechanical seal 512 at the front end portion of the front bearing portion 511, it is possible to prevent water from entering between the bearing unit 500 and the drum shaft 300.

The stator 120 of the drive motor 100 is fixed to the mounting boss 526 of the rear unit 520. At this time, the screw 540 is blocked by the mounting hole 526a through the screw hole 122.

The bearing unit 500 is fixed to the rear surface of the outer tub 20 by a fixing method such as screwing. In a state where the driving unit 30 has been mounted in the outer tub 20, the wing shaft 200 and the drum shaft 300 face the inside of the outer tub 20. The drum 22 is fixed to the drum shaft 300, and the agitating body 24 is fixed to the wing shaft 200.

Referring to Figures 8 through 10, the clutch mechanism portion 600 includes a clutch body 610, a clutch spring 620, a clutch lever 630, a lever support 640, a clutch drive 650, and a mounting plate 660. The clutch spring 620, the clutch lever 630, the lever support 640, the clutch driving device 650, and the mounting plate 660 constitute a moving mechanism portion DM that moves the clutch body 610 in the forward and backward directions.

The clutch body 610 has a substantially disk shape. An annular rack 611 is formed on the outer peripheral surface of the front end portion of the clutch body 610. The rack 611 is formed to be engaged with the rack 525 at the rear end portion of the rear unit 520. The rack 611 corresponds to the first "" joint portion of the present invention. Further, a flange portion 612 is formed on the outer circumferential surface of the clutch body 610 behind the rack 611. Further, a ring-shaped engagement flange portion 613 is formed at the rear end portion of the clutch body 610. The engaging flange portion 613 has the same shape as the engaged concave portion 114 of the rotor 110, and has an uneven portion 613a over the entire circumference at the outer peripheral portion. When the engaging flange portion 613 is inserted into the engaged concave portion 114, the uneven portions 613a, 114a are engaged with each other. The engagement flange portion 613 corresponds to the second engagement portion of the present invention.

A shaft hole 614 into which the carrier shaft 442 is inserted is formed at a central portion of the front surface of the clutch body 610. A rack 614a is formed on the inner circumferential surface of the shaft hole 614. Rack 614a and rack 442c of carrier shaft 442 Engage. Thereby, the clutch body 610 is allowed to move in the forward and backward directions with respect to the carrier shaft 442, and the rotation in the circumferential direction is restricted. Further, an annular receiving groove 615 is formed on the outer surface of the shaft hole 614 on the front surface of the clutch body 610. The receiving groove 615 has a depth reaching the rear end portion. As shown in FIG. 2, a clutch spring 620 is housed in the housing groove 615. The clutch spring 620 corresponds to the elastic member of the present invention. One end of the clutch spring 620 is in contact with the spring impact plate 524 of the rear unit 520, and the other end is in contact with the bottom surface of the receiving groove 615.

The clutch lever 630 includes a substantially semicircular upper rod 631 along the outer peripheral surface of the lower half of the clutch body 610, and a lower rod 632 extending downward from the lowermost portion of the upper rod 631. A pressing portion 633 that comes into contact with the rear surface 612a of the flange portion 612 of the clutch body 610 and pushes the flange portion 612 forward is formed at the right and left upper end portions of the upper rod 631. The pressing portion 633 corresponds to the pressing member of the present invention. Further, in Fig. 9 (c), the clutch body 610 is drawn for convenience of explanation.

The fulcrum 634 is fixed to the clutch lever 630. The support shaft 634 penetrates the left and right of the clutch lever 630, and both ends thereof are protruded from the clutch lever 630 to the left and right.

The lever support 640 supports the clutch lever 630 in a rotatable manner. The lever support 640 includes a bottom plate 641 and an arm piece 642 that rises from both ends of the bottom plate 641. A shaft hole 643 is formed in the arm piece 642. The fulcrum 634 passes through the fulcrum hole 643. Thereby, the clutch lever 630 can be rotated forward and backward in the center of the support shaft 634.

Spring 644 is interposed between clutch lever 630 and lever support 640. One end of the spring 644 is fixed to the mounting shaft 645 of the lever holder 640, and the other end is inserted through the insertion hole 635 of the clutch lever 630, and is fixed to the mounting shaft 636 provided on the clutch lever 630 in the same manner as the insertion hole 635. In a state where the clutch mechanism portion 600 is mounted, the spring 644 is in a stretched state, and the lower end of the lower rod 632 of the clutch lever 630 is pulled by the elastic force of the spring 644 toward the forward direction.

The clutch driving device 650 includes a torque motor 651 and a disk-shaped cam 652 that rotates around the horizontal shaft by the torque of the torque motor 651. The upper surface of the cam 652 is in contact with the lower end of the lower rod 632. The upper surface of the cam 652 includes: a first contact surface 652a having a high height disposed on one end side, a second contact surface 652b having a low height disposed on the other end side, and a first contact surface 652a and a second contact surface 652b An inclined surface 652c that is connected to each other.

The rod support 640 and the clutch drive unit 650 are fixed to the mounting plate 660 by a fixing method such as screwing. The mounting plate 660 is fixed to the mounting boss 516 of the front unit 510 by screws.

When the form of the driving unit 30 is switched from the second mode to the first mode, as shown in FIG. 10( a ), The cam 652 is rotated by the torque motor 651 such that the first contact surface 652a is located above and the second contact surface 652b is positioned below. As the cam 652 rotates, the lower end of the lower rod 632 is sequentially pressed by the inclined surface 652c and the first contact surface 652a to move rearward. The clutch lever 630 rotates forward about the support shaft 634, and the upper lever 631 moves forward. The pressing portion 633 of the upper rod 631 presses the flange portion 612 of the clutch body 610 forward, and the clutch body 610 resists the elastic force of the clutch spring 620 from moving forward.

On the other hand, when the form of the drive unit 30 is switched from the first mode to the second mode, as shown in FIG. 10(b), the cam 652 is positioned above the second contact surface 652b by the torque motor 651. A contact surface 652a is rotated in a downward manner. As the cam 652 rotates, the lower end of the lower rod 632 moves forward along the inclined surface 652c and the second contact surface 652b by the elastic force of the second spring 647. The clutch lever 630 rotates rearward about the spindle 634, and the upper lever 631 moves rearward. The pressing portion 633 of the upper rod 631 is separated from the flange portion 612 of the clutch body 610, and the clutch body 610 is moved rearward by the elastic force of the clutch spring 620.

Drum washing machine 1 Perform washing operation for various operating procedures. The washing operation includes a washing process, an intermediate dewatering process, a rinsing process, and a final dewatering process.

Figs. 11(a) and (b) are views for explaining the operation of the drive unit 30, the drum 22, and the agitating body 24 in the washing step and the rinsing step. Fig. 12 (a) and (b) are diagrams for explaining the operations of the drive unit 30, the drum 22, and the agitating body 24 in the intermediate dewatering step and the final dewatering step.

In the washing step and the rinsing step, the form of the drive unit 30 is switched to the first form. By switching to the first configuration, as shown in FIG. 10(a), when the clutch body 610 is moved forward, as shown in FIG. 11(a), the rack 611 of the clutch body 610 and the rack 525 of the bearing unit 500 are stuck. Hehe. Thereby, since the circumferential rotation of the clutch body 610 with respect to the bearing unit 500 is restricted and becomes a non-rotatable state, the carrier shaft 442 of the planetary gear mechanism 400, that is, the carrier 440 is fixed in a non-rotatable manner. status. In such a state, when the rotor 110 rotates, the wing shaft 200 rotates at a rotational speed equal to the rotational speed of the rotor 110, and the agitating body 24 coupled to the wing shaft 200 also rotates at a rotational speed equal to the rotational speed of the rotor 110. . The sun gear 410 of the planetary gear mechanism 400 rotates with the rotation of the wing shaft 200. As described above, since the carrier 440 is in a fixed state, the first gear 431 and the second gear 432 of the planetary gear 430 rotate in the same direction and in the opposite direction as the sun gear 410, respectively, and the internal gear 420 rotates in the same direction as the sun gear 410. Thereby, the drum shaft 300 fixed to the internal gear 420 rotates. Since the planetary gear mechanism 400 is decelerated, the drum shaft 300 is compared to the wing shaft 200 The slow rotation speed rotates in the same direction as the wing shaft 200, and the drum 22 fixed to the drum shaft 300 rotates in the same direction as the agitating body 24 at a rotation speed slower than that of the agitating body 24. In other words, the agitating body 24 rotates in the same direction as the drum 22 at a rotational speed faster than the drum 22. Further, the rotational speed of the rotor 110 and the reduction ratio of the planetary gear mechanism 400 can be appropriately set so that the agitating body 24 can be rotated at a rotational speed at which the laundry can be rubbed or agitated without damage, and the rotational speed of the drum 22 becomes The centrifugal force of the laundry acting on the drum 22 becomes smaller than the rotational speed of gravity.

In the washing step and the rinsing step, the driving motor 100 alternately performs the right rotation and the left rotation in a state where the water is stored in the outer tank to a predetermined water level below the input port 11. Thereby, the drum 22 and the agitating body 24 alternately perform the right rotation and the left rotation in a state where the rotation speed of the agitating body 24 is faster than the rotation speed of the drum 22. The laundry in the drum 22 is dropped onto the inner peripheral surface of the drum 22 by being lifted up by the flapper 23 and dropped. Further, at the rear of the drum 22, the laundry comes into contact with the blades 24a of the rotating agitating body 24, and the laundry is rubbed with the blades 24a or the laundry is agitated by the blades 24a. Thereby, the laundry is washed or rinsed.

Next, in the intermediate dehydration step and the final dehydration step, the form of the drive unit 30 is switched to the second form. By switching to the second mode, as shown in FIG. 10(b), when the clutch body 610 is moved rearward, as shown in FIG. 12(a), the engaging flange portion 613 of the clutch body 610 is fitted into the card of the rotor 110. The concave portion 114 and the uneven portion 613a of the engagement flange portion 613 are engaged with the uneven portion 114a of the engaged concave portion 114. Further, even when the engagement flange portion 613 is fitted into the engaged recessed portion 114, the clutch spring 620 is maintained in a collapsed state, and the engagement flange portion 613 is pressed against the engaged recessed portion 114 by the elastic force of the clutch spring 620. . When the engaging flange portion 613 is engaged with the engaged concave portion 114, the pressing portion 633 is separated from the clutch body 610.

When the engagement flange portion 613 is engaged with the engaged portion 114, the circumferential rotation of the clutch body 610 with respect to the rotor 110 is restricted, and the clutch body 610 is rotatable with the rotor 110. In such a state, when the rotor 110 rotates, the wing shaft 200 and the clutch body 610 rotate at a rotational speed equal to the rotational speed of the rotor 110. At this time, the sun gear 410 of the planetary gear mechanism 400 and the carrier 440 rotate at a rotation speed equal to that of the rotor 110. Thereby, the internal gear 420 rotates at the same rotational speed as the sun gear 410 and the carrier 440, and the drum shaft 300 fixed to the internal gear 420 rotates at the same rotational speed as the rotor 110. That is, in the drive unit 30, as shown by dashed-dotted lines in Figs. 12(a) and (b), the wing shaft 200, the planetary gear mechanism 400, and the drum shaft 300 rotate integrally. Thereby, the drum 22 and the agitating body 24 are rotated in the body. In addition, the clutch spring 620 is also The clutch body 610 is rotated.

In the intermediate dehydration step and the final dehydration step, the rotor 110, that is, the drum 22 and the agitating body 24, rotate so that the centrifugal force acting on the laundry in the drum 22 is much larger than the rotational speed of gravity. The laundry is pressed onto the inner peripheral surface of the drum 22 by dehydration by the action of the centrifugal force.

As described above, according to the present embodiment, in the washing step and the rinsing step, the drum 22 and the agitating body 24 are rotated such that the rotational speed of the agitating body 24 is faster than the rotational speed of the drum 22. Thereby, the laundry in the drum 22 is not only hit by the agitation generated by the baffle 23 to the inner peripheral surface of the rolling wheel 22, but also by the blades 24a of the rotating agitating body 24. Thereby, the cleaning performance and the rinsing performance can be improved as compared with the structure in which the laundry is stirred only by the baffle 23.

Further, according to the present embodiment, as the configuration of the drive unit 30 for rotating the agitating body 24 faster than the drum 22, the agitating body 24 can be rotated at a rotation speed equal to that of the rotor 110, and compared with the agitation. The body 24 requires a larger torque, and the drum 22 is rotated by decelerating the rotation of the rotor 110. Thereby, the drum 22 is rotated at a rotation speed equal to that of the rotor 110, and the agitator 24 is rotated by increasing the rotation of the rotor 110, whereby the drum 22 and the agitator 24 can be driven to be driven. The torque generated by the motor 100 can reduce the power consumption of the drive motor 100.

Further, according to the present embodiment, the rotor 110 of the drive motor 100 is coupled to the agitating body 24 via a wing shaft 200. Therefore, unlike the structure in which the rotating shaft of the rotor 110 and the rotating shaft of the agitating body 24 are respectively disposed and coupled to each other, when the driving unit 30 is assembled, it is not necessary to align the axes of the centers of the two rotating shafts. Thereby, the assembly of the drive unit 30 becomes easy. In addition, there is no need to worry about axis misalignment between the two axes of rotation.

Further, according to the present embodiment, the space generated between the first rolling bearing 513 and the second rolling bearing 523 is used as the arrangement space of the planetary gear mechanism 400, so that the load generated by the drum 22 is favorably supported by the drum shaft 300, and thus The size of the drive unit 30 is reduced in the axial direction of the drum shaft 300. Thereby, the outer tub 20 and the drum 22 can be made larger in the front-rear direction, so that the washing capacity can be changed and, according to the present embodiment, the drum shaft 300 is fixed to the inner gear 420, and the carrier provided on the carrier 440 is provided. The front end portion 442b of the shaft 442 protrudes toward the outer surface of the drum shaft 300, and the clutch mechanism portion 600 is associated with the protruding front end portion 442b, thereby switching the operation of the planetary gear mechanism 400, and the flap shaft 200 and the drum shaft 300 are respectively The first form of rotation and the wing shaft 200 and The drum shaft 300 switches the form of the drive unit 30 between the second forms of body rotation. Therefore, as a result of the configuration in which the planetary gear mechanism 400 is sandwiched by the first rolling bearing 513 and the second rolling bearing 523, even when the planetary gear mechanism 400 is housed in the drum shaft 300, the structure can be satisfactorily performed. Switching between a form and a second form. Further, by adjusting the number of teeth of the sun gear 410 and the internal gear 420, the reduction ratio of the rotor 110 and the drum shaft 300 can be set, and a reduction ratio of a wide range can be set.

Further, according to the present embodiment, since the planetary gear 430 is constituted by the first gear 431 and the second gear 432, when the drive unit 30 is formed by fixing the internal gear 420 to the drum shaft 300, the drum shaft 300 is caused. When the structure is rotated and decelerated, the drum shaft 300 can be rotated in the same direction as the wing shaft 200. Thereby, since the stirring force generated by the agitating body 24 can be applied in the same direction of rotation of the drum 22, the stirring force of the laundry in the drum 22 can be increased.

According to the present embodiment, the clutch body 610 that is fitted into the distal end portion 442b of the carrier shaft 442 that protrudes to the outside of the drum shaft 300 is moved in the axial direction of the drum shaft 300 by the moving mechanism portion DM, so that the clutch body is provided. The rack 611 of the 610 is engaged with the rack 525 of the bearing unit 500, or the engaging flange portion 613 of the clutch body 610 is engaged with the engaged portion 114 of the rotor 110, so that the through gear can be specifically realized. The frame shaft 422, which is the planetary carrier 440, is associated with the clutch mechanism portion 600 in which the form of the drive unit 30 is switched between the first form and the second form. Further, since the rack 525 that is engaged with the rack 611 of the clutch body 610 is formed in the rear unit 520 in which the second rolling bearing 523 is disposed concentrically with the carrier shaft 442 in which the clutch body 610 is fitted, the tooth can be accurately positioned. The center of the bar 611 coincides with the center of the rack 525. Thereby, the racks 611 and 525 can be engaged with each other with high precision.

Further, according to the present embodiment, when the clutch body 610 is moved by the elastic force of the clutch spring 620, the engagement flange portion 613 is engaged with the engaged portion 114, and the clutch body 610 and the rotor 110 are engaged by the engagement. When the rotation is started, the pressing portion 633 is in a state of being separated from the clutch body 610. Therefore, the rotation of the rotor 110 and the clutch body 610 is not hindered by the contact of the pressing portion 633 with the clutch body 610.

Further, according to the present embodiment, the bearing unit 500 is configured to include a planetary gear mechanism in the axial direction of the drum shaft 300 by a front unit 510 including a first rolling bearing 513 and a rear unit 520 including a second rolling bearing 523. The drum shaft 300 of 400 is covered from the front and rear sides. In the case where the bearing unit 500 is not divided, as shown in FIG. 13, in the bearing unit 500, It is ensured that the opening O of the drum shaft 300 in which the planetary gear mechanism 400 is enclosed is inserted, for example, a structure in which a second rolling bearing 523 larger than the outer diameter of the accommodating portion 300c of the drum shaft 300 is used, and the drum is used The wall thickness of the rear shaft portion 300b of the shaft 300 is increased by the amount by which the outer diameter of the second rolling bearing 523 is increased. According to the configuration of the present embodiment, since the drum shaft 300 of the inner planetary gear mechanism 400 can be housed inside the bearing unit 500 by the combination of the front unit 510 and the rear unit 520, it is possible to avoid the use of the first large one beyond the need. The rolling bearing 513 and the second rolling bearing 523 or the roller shaft 300 are unnecessarily heavy due to an increase in wall thickness.

Further, according to the present embodiment, since the front unit 510 and the rear unit 520 are coupled by the socket fitting, the center of the first rolling bearing 513 can be made even in the case of the structure in which the bearing unit 500 is divided. P1 and the center P2 of the second rolling bearing 523 are accurately matched. Therefore, it is possible to prevent the drum shaft 300 from being smoothly rotated because the center P1 of the first rolling bearing 513 is displaced from the second rolling bearing 523.

Further, according to the above embodiment, since the stator 120 of the drive motor 100 is fixed to the rear unit 520 in which the second rolling bearing 523 is provided, the center of the stator 120 and the center P2 of the second rolling bearing 523 can be accurately matched. Since the center of the second rolling bearing 523 coincides with the center of the rotor 110 fixed to the wing shaft 200, the center of the stator 120 is in good agreement with the center accuracy of the rotor 110. Thereby, the gap S (refer to Fig. 2) between the rotor 110 and the stator 120 can be maintained, so that the drive motor 100 can be stably rotated.

Although the embodiment of the present invention has been described above, the present invention is not subject to any of the above-described embodiments. For example, in the above embodiment, the clutch is restrained by the engagement of the rack 611 of the clutch body 610 with the rack 525 of the bearing unit 500. The body 610 is rotated relative to the circumferential direction of the bearing unit 500. Further, the engagement of the engaging flange portion 613 of the clutch body 610 with the engaged portion 114 of the rotor 110 restricts the circumferential rotation of the clutch body 610 with respect to the rotor 100. However, the configuration in which the front end portion of the clutch body 610 is engaged with the bearing unit 500 and the configuration in which the rear end portion of the clutch body 610 is engaged with the rotor 110 are not limited to the above-described embodiments, and other configurations may be employed. For example, a structure may be formed in which a projection is formed at the front end portion and the rear end portion of the clutch body 610, and a recess or a hole is formed in the bearing unit 500 and the rotor 110 to embed the projection in the recess or the hole.

Further, in the above embodiment, the covering portion 521 covering the accommodating portion 300c of the drum shaft 300 is provided in the rear unit 520. However, the cover portion 521 may also be disposed at the front unit 510, and the cover portion 521 is also It may be arranged to be separated at the front unit 510 and the rear unit 520.

Further, in the above embodiment, the fitted portion 514 is provided in the front unit 510, and the fitting rib 527 is provided in the rear unit 520. However, it is also possible to provide the fitting rib 527 in the front unit 510 and the fitted recess 514 in the rear unit 520. Further, in the above embodiment, the fitting ribs 527 are in contact with the outer peripheral surfaces 527a and 514a of the fitted recessed portions 514 at the time of fitting. However, the fitting ribs 527 and the fitted recessed portions 514 may be configured to be in contact with each other's inner peripheral surface, or may be configured such that both the inner peripheral surface and the outer peripheral surface are in contact with each other. In this case, when the inner circumferential surfaces are in contact with each other, the inner circumferential surfaces each have a circular shape concentric with the rolling bearing corresponding to each inner circumferential surface. Further, the circumferential surface that is in contact with each other may not be completely circular, but may be a shape in which the circle is interrupted in the middle. That is, the circumferential surface that is in contact with each other may also be a circular arc shape. That is, each of the circumferences is formed as long as the circumferential surface having the circular or circular shape which is concentric with the first rolling bearing 514 and the circumferential surface having the circular or circular arc shape concentric with the second rolling bearing 523 can be performed. The shape of the face can be anything.

Further, in the above embodiment, the drum 22 is rotated about the tilt axis that is inclined with respect to the horizontal direction. However, the drum washing machine 1 may be configured to rotate the drum 22 around the horizontal axis.

Further, although the drum washing machine 1 of the above embodiment does not have a drying function, the present invention can also be applied to a drum washing machine having a drying function, that is, a drum washing and drying machine.

Further, the embodiments of the present invention can be variously modified as appropriate within the scope of the technical idea described in the claims.

Description of the reference numerals

10: housing; 20: outer groove; 22: roller; 24: agitating body (rotating body); 24a: blade (projection); 30: drive unit (drive unit); 100: drive motor; 110: rotor; 114: engaged recess (second engaged portion); 120: stator; 200: wing shaft (first rotating shaft); 202: limiting ring; 300: drum shaft (second rotating shaft); 300a: front shaft Part (first shaft portion); 300b: rear shaft portion (second shaft portion); 300c: housing portion; 400: planetary gear mechanism (shifting mechanism, speed reducing mechanism); 410: sun gear; 420: internal gear; 430: Planetary gear; 431: first gear; 432: second gear; 440: planetary carrier; 442: carrier shaft (shaft portion); 500: bearing unit; 510: front unit (first unit); 513: a rolling bearing (first bearing); 514: fitted recess; 514a: outer peripheral surface (first circumferential surface); 520: rear unit (second unit); 523: second rolling bearing (second bearing); 525: Rack (first engaged portion); 526: mounting bushing (fixing portion); 527: fitting rib (protruding portion) ; 527a: outer peripheral surface (second circumferential faces); 600: clutch mechanism portion; 610: clutch body; 611: a rack (first One engaging portion); 613: engaging flange portion (second engaging portion); 620: clutch spring (elastic member); 630: clutch lever; 633: pressing portion (urging member); 640: rod supporting 650: clutch drive; 660: mounting plate; DM: moving mechanism.

Claims

Claim

A drum washing machine characterized by comprising:

The outer groove is disposed in the housing;

a drum disposed in the outer groove and rotatable about a horizontal axis or an inclined axis inclined with respect to a horizontal direction;

a baffle disposed on an inner circumferential surface of the drum;

a rotating body disposed at a rear portion of the drum and having a protrusion on the surface in contact with the laundry; and

a driving unit that rotates the drum and the rotating body such that a rotation speed of the rotating body is faster than a rotation speed of the drum

Wherein the driving part comprises:

Drive motor

a first rotating shaft coupled to the rotating body, transmitting torque of the driving motor to the rotating body, and a shifting mechanism for shifting a rotation of a rotor of the drive motor;

a second rotating shaft coupled to the drum, transmitting torque of the driving motor to the drum, and enclosing the first rotating shaft and the speed reducing mechanism;

a bearing unit having a first bearing and a second bearing disposed to sandwich the shifting mechanism, and the second rotating shaft is rotatably supported by the first bearing and the second bearing,

The second rotating shaft includes: a first shaft portion supported by the first bearing; a second shaft portion supported by the second bearing; and a receiving portion than the first shaft portion and the second portion The shaft portion is further bulged outward and accommodates the shifting mechanism.

The bearing unit includes a first unit including the first bearing and a second unit including the second bearing, the first unit and the second unit being in an axial direction of the second rotating shaft, from the The sides of the accommodating section are combined.

2. The drum type washing machine according to claim 1, wherein

The first unit has a first circumferential surface having a circular or circular arc shape concentric with the first bearing, and the second unit has a second circumferential surface, the second circumferential surface Having a circular or circular arc concentric with the second bearing,

The first unit and the second unit are coupled by socket fitting of the first circumferential surface and the second circumferential surface.

The drum type washing machine according to claim 1 or 2, wherein the second unit of the bearing unit is located on a side of the drive motor, and the second unit is provided with a motor for fixing the motor The fixing portion of the stator.

The drum type washing machine according to any one of claims 1 to 3, wherein the speed reduction mechanism includes: a sun gear that rotates in accordance with rotation of the drive motor rotor; and an annular internal gear, Surrounding the sun gear; a plurality of planet gears between the sun gear and the internal gear; and a planet carrier that rotatably holds the planet gears,

The second rotating shaft is fixed to the internal gear and rotates with the rotation of the internal gear, the planetary carrier includes a shaft portion coaxial with the second rotating shaft and a front end portion Said second rotating axis, said rotor side protruding,

The driving portion further includes a clutch mechanism portion,

The clutch mechanism portion is configured to switch the shape of the driving portion between the first form and the second form in relation to a front end portion of the shaft portion protruding from the second rotating shaft, wherein the first portion In a state in which the shaft portion is in a non-rotatable state, the rotation speed of the second rotation shaft is slower than the rotation speed of the first rotation shaft in accordance with the reduction ratio of the speed change mechanism. The first rotating shaft and the second rotating shaft are rotated, and in the second aspect, the first rotating shaft and the first rotating shaft are caused by the shaft portion being rotated together with the rotor The speed reduction mechanism and the second rotating shaft rotate integrally at a rotation speed equal to a rotation speed of the rotor.

5. The drum type washing machine according to claim 4, wherein

The clutch mechanism portion includes: a clutch body that is fitted into the front end portion, movement relative to the front end portion in an axial direction of the shaft portion is permitted and rotation in a circumferential direction of the shaft portion is restricted; and movement a mechanism portion that moves the clutch body in the axial direction,

a first engaging portion and a second engaging portion are respectively disposed at an end portion of the clutch body on the bearing unit side and an end portion on the rotor side.

The second unit located on the side of the drive motor is provided with a first engaged portion,

Providing a second engaged portion in the rotor,

The clutch body is opposite to the second when the clutch body is moved to the second unit side by the moving mechanism portion and the first engaging portion is engaged with the first engaged portion The rotation of the unit in the circumferential direction is restricted, and the shaft portion becomes in a state in which it cannot rotate. When the clutch body moves to the rotor side by the moving mechanism portion and the second engaging portion engages with the second engaged portion, the clutch body is circumferential with respect to the rotor The rotation of the direction is restricted, and the shaft portion is rotatable together with the rotor.

6. The drum type washing machine according to claim 5, wherein

The moving mechanism portion includes:

An elastic member interposed between the clutch body and the bearing unit to move the clutch body to the rotor side by elastic force to engage the second engaging portion with the second engaged portion And a pressing member that moves the clutch body toward the bearing unit side by pushing the clutch body, and in a state where the first engaging portion is engaged with the first engaged portion The clutch body is in contact with the clutch body, and is separated from the clutch body in a state in which the second engagement portion is engaged with the second engaged portion.