WO2015131482A1

WO2015131482A1 - Drum washing machine

Info

Publication number: WO2015131482A1
Application number: PCT/CN2014/083631
Authority: WO
Inventors: 竹内晴美; 广田弘美; 中本重阳; 田中启之
Original assignee: 海尔集团公司; 海尔亚洲国际株式会社; 青岛海尔洗衣机有限公司
Priority date: 2014-03-06
Filing date: 2014-08-04
Publication date: 2015-09-11
Also published as: JP2015167663A; JP6282492B2; CN105102707B; CN105102707A

Abstract

The present invention provides a drum washing machine capable of improving washing performance. The drum washing machine (1) comprises: an outer tank (20), disposed in a housing (10); a drum (22), disposed in the outer tank (20) and capable of rotating about an inclined shaft tilting relative to the horizontal direction; a baffle (23), disposed on the inner circumferential surface of the drum (22); an agitator (24), located in the rear part of the drum (22) and rotating coaxially with the drum (22), the surface of the agitator (24) being provided with blades (24a) in contact with laundry; and a driving unit (30), driving the drum (22) and the agitator (24) to rotate in the same direction in a manner that the rotating speed of the agitator (24) is higher than that of the drum (22).

Description

Drum washing machine

Technical field

The present invention relates to a drum washing machine. The drum washing machine can be carried out continuously from washing to drying, or can be washed without drying. 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).

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

As described above, in the structure in which the laundry is stirred by the baffle, the mechanical force acting on the laundry is likely to be smaller than that of the fully automatic washing machine in which the laundry is difficult to reciprocate, and the washing performance is liable to lower.

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 improving washing performance.

Solution to solve the problem

A drum washing machine of a main aspect of the present invention includes: an outer groove disposed in a casing; and a drum disposed in the outer groove and rotatable about a horizontal axis or an inclined axis inclined with respect to a horizontal direction; Provided on an inner circumferential surface of the drum; a rotating body disposed at a rear portion of the drum so as to rotate coaxially with the drum, having a protruding portion on the surface in contact with the laundry; and a driving portion, a barrel Rotate in a fast rotation.

According to the above configuration, the laundry in the drum is not only hit by the baffle agitation to the inner peripheral surface of the drum but also rubbed or agitated by the projecting portion of the rotating rotating body. Therefore, with only the baffle stirring Compared with the structure of the laundry, the cleaning performance can be improved.

In the drum washing machine of the present type, the drive unit may be disposed behind the outer tub, and includes a drive motor and a transfer of the drive motor to the rotary body and the drum. The transmission mechanism of the moment. In this case, a structure may be employed in which the transmission mechanism portion includes a first rotation shaft, a speed reduction mechanism, and a second rotation shaft, wherein the first rotation shaft is rotated by the torque of the drive motor, and The rotation is transmitted to the rotating body, and the speed reducing mechanism rotates the first rotating shaft rotating shaft coaxially, and transmits the rotation to the drum.

According to the above configuration, the drum that requires more torque than the rotating body is rotated by decelerating the rotation of the driving motor, so that the torque generated by the driving motor when the drum and the rotating body are driven can be reduced, so that the power consumption of the driving motor can be reduced. .

In the case of the above configuration, a configuration may be adopted in which the lower portion of the first rotating shaft may be configured such that the speed reducing mechanism includes a planetary gear mechanism having a planetary gear mechanism having a sun gear; an annular inner gear surrounding the sun gear; a plurality of planet gears meshing with both the sun gear and the inner gear, and revolving around the sun gear; and a planet carrier, accompanied by The planetary gears rotate in revolution, and the sun gear is disposed on the first rotating shaft. Further, a configuration may be employed in which the second rotating shaft encloses the first rotating shaft, the front end portion is coupled to the drum, and the rear end portion is coupled to the planetary carrier.

When such a configuration is adopted, since the rotor and the rotating body of the drive motor are coupled by one first rotating shaft, the structure in which the rotating shaft of the rotor and the rotating shaft of the rotating body are respectively connected and connected to each other is different, and when the driving portion is assembled There is no need to align the axes of the centers of the two axes of rotation. Therefore, assembly of the drive unit becomes easy. In addition, there is no need to worry about the axis deviation generated between the two rotating shafts.

Further, since the speed reduction mechanism that decelerates the rotation of the first rotating shaft and transmits the second rotating shaft to the second rotating shaft is constituted by the planetary gear mechanism, the gear of the structural speed reducing mechanism is not aligned in the axial direction of the first rotating shaft and the second rotating shaft. The size of the transmission mechanism portion in the axial direction, that is, the drive portion can be reduced. Thereby, since the outer tub and the drum can be enlarged in the front-rear direction, the washing capacity can be increased.

In the case of the above configuration, the following configuration may be employed, that is, the drive unit further includes a clutch mechanism portion. In this case, the clutch mechanism unit switches the form of the drive unit between the first mode and the second mode. In the first aspect, the internal gear is fixed so as not to be rotatable. The first rotating shaft rotates at a rotational speed equal to a rotational speed of the rotor, and The second rotating shaft rotates at a rotational speed decelerated by the planetary gear mechanism, and the second form rotates the internal gear together with the rotor, thereby enabling the first rotating shaft and the second The rotating shaft and the planetary gear mechanism integrally rotate at a rotational speed equal to the rotational speed of the rotor.

According to this configuration, in the spin-drying process, by switching the form of the driving portion from the first form to the second form, the drum and the rotating body can be integrally rotated at high speed. Thereby, the laundry in the drum is not stirred by the rotating body, and the washing of the laundry can be appropriately performed.

In the case of the above configuration, the drive unit may further include a bearing unit that rotatably supports the second rotating shaft. Further, a configuration may be employed in which the clutch mechanism portion includes: a cylindrical clutch body surrounding an outer circumference of the internal gear, and movement in a forward and backward direction with respect to the internal gear is allowed and circumferentially The rotation is restricted; and the moving mechanism portion moves the clutch body in the front-rear direction, and the first engaging portion and the second engaging portion are respectively disposed at the front end portion and the rear end portion of the clutch body, and the bearing unit is And the rotor is provided with a first engaged portion and a second engaged portion, respectively. In this case, when the clutch body is moved forward by the moving mechanism portion to engage the first engaging portion with the first engaged portion, the clutch body is opposite to the bearing unit The circumferential rotation is restricted, and the internal gear is fixed and cannot be rotated. On the other hand, when the clutch body moves rearward by the moving mechanism portion and the second engaging portion is engaged with the second engaged portion, the clutch body is oriented with respect to the rotor The circumferential rotation is limited and the internal gear can rotate with the rotor.

In this way, since the clutch mechanism portion is configured to move the tubular clutch body in the front-rear direction on the outer circumference of the inner gear, the planetary gear mechanism can be disposed in the axial direction of the first rotating shaft and the second rotating shaft. The configuration space is utilized for the movement space of the clutch body. Therefore, the size of the driving portion of the first rotating shaft and the second rotating shaft in the axial direction can be further reduced.

In the case of the above configuration, the clutch body may be disposed between the bearing unit and the drive motor, and the rear portion of the clutch body may be housed inside the drive motor.

According to this configuration, since the clutch body and the drive motor are overlapped in the axial direction of the first rotating shaft and the second rotating shaft, the size of the driving portion in the axial direction can be further reduced.

In the case of the above configuration, the moving mechanism portion may include an elastic member interposed between the clutch body and the planetary gear mechanism to cause the clutch body to pass the elastic force. Moving backward, the second engaging portion is engaged with the second engaged portion; and pressing member, the clutch body is moved forward by pressing the clutch body, so that the first One card card The first engaged portion is coupled to the first engaged portion, and is separated from the clutch body in a state in which the second engaging portion is engaged with the second engaged portion.

If such a structure is used, the clutch body is moved by the elasticity of the elastic member, thereby engaging the second engaging portion with the second engaged portion, and the clutch body rotates the clutch body together with the rotor. At this time, 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 achieve an improvement in cleaning performance.

The effects and significance of the present invention will be further clarified by the description of the embodiments shown 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 embodiments. BRIEF DESCRIPTION OF DRAWINGS FIG. 2 is a cross-sectional view showing a configuration of a drive unit according to an embodiment.

3 is a cross-sectional view showing a configuration of a drive unit according to an embodiment.

4 is a front view of the rotor showing a configuration of a rotor of a drive motor according to the embodiment. Fig. 5 is a front elevational view showing the clutch plate of the bearing unit of the bearing unit according to the embodiment.

Fig. 6 is a view showing a configuration of a clutch body according to an embodiment, and a state in which a guide rib of a clutch body is fitted into a groove portion of an outer circumferential surface of the internal gear. 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 is provided with a casing 10 constituting an exterior. The front surface 10a of the casing 10 is inclined upward from the central portion, and an inclined inlet surface 11 is formed on the inclined surface. The entrance 11 is covered by a door 12 that is freely 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 lowered relative to the horizontal direction. The inclination angle of the groove 20 and the drum 22 can be used 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 are closed by the door 12 together with the input port 11. 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 disc shape. On the surface of the agitating body 24, a plurality of blades 24a radially extending from the central portion are formed. 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 accommodated freely 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 cartridge 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.

2 and 3 are cross-sectional views showing the structure of the drive unit 30. Fig. 2 shows a state in which the form of the drive unit 30 is switched to the first mode, and Fig. 3 shows a state in which the form of the drive unit 30 is switched to the second form. 4 is a front view of the rotor 110 showing the structure of the rotor 110 of the drive motor 100. FIG. 5 is a front view of the clutch plate 520 showing the structure of the clutch plate 520 of the bearing unit 500. Figure 6 (a) and FIG. 6(b) are a rear view and a front view of the clutch body 610 showing the structure of the clutch body 610. (c) of FIG. 6 is a view showing a state in which the guide rib 615 of the clutch body 610 is fitted into the groove portion 421 of the outer circumferential surface of the internal gear 420.

The drive unit 30 is composed of 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, the drum shaft 300, and the planetary gear mechanism 400 constitute a transmission mechanism portion TR that transmits torque generated by the drive motor 100 to 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 is equivalent to the first axis of rotation of the present invention. The planetary gear mechanism 400 decelerates the rotation of the wing shaft 200 and transmits it to the drum shaft 300. 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 freely rotatable manner. The clutch mechanism unit 600 switches between the first mode and the second mode in which the blade unit 200 is rotated at a rotation speed equal to the rotation speed of the drive motor 10. The rolling axis 300 is rotated at a rotational speed that is decelerated by the planetary gear mechanism 400. In the second aspect, the wing shaft 200, the rolling shaft 300, and the planetary gear mechanism 400 can be integrally rotated at a rotational speed equal to that of the drive motor 10. .

The drive motor 100 is an outer rotor type DC brushless motor having a rotor 110 and a stator 120. The rotor 110 is formed in a bottomed cylindrical shape, and on its inner peripheral surface, the permanent magnets 111 are arranged throughout the entire circumference. As shown in Fig. 4, an annular clutch plate 112 is provided at the center of the rotor 110. Annular serrations 113 are formed on the front surface of the clutch disc 112 toward the front. The serrations 113 correspond to the second engaged portion of the present invention. Moreover, in Fig. 4, the groove portion of the serrations 113 is painted gray for convenience. 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.

The drum shaft 300 has a hollow shape. Inside the drum shaft 300, sliding bearings 301, 302 are provided on the front and rear portions, respectively, and a mechanical seal 303 is provided on the front end portion.

A wing shaft 200 is inserted inside the drum shaft 300. The outer peripheral surface of the wing shaft 200 slides between the slide shafts 301, 302. Thereby, the wing shaft 200 smoothly rotates in the drum shaft 300. Furthermore, the intrusion of water between the drum shaft 300 and the wing shaft 200 is prevented by the mechanical seal 303.

The planetary gear mechanism 400 includes: a sun gear 410; an annular internal gear 420 surrounding the sun gear 410; and a plurality of planetary gears 430 meshing with both the sun gear 410 and the internal gear 420, and in the sun The circumference of the gear 410 revolves; the carrier 440 holds the planetary gears 430 in a rotationally movable manner, and rotates with the revolution of the planetary gears 430; and the support disk 450 supports the rear of the planetary carrier 440.

The sun gear 410 is fixed to a portion in the middle of the wing shaft 200. Further, the rear end portion of the drum shaft 300 is fixed to the central portion of the front surface of the planetary carrier 440. Thus, a planetary gear mechanism 400 is disposed between the wing shaft 200 and the drum shaft 300. Further, a rotor 110 that drives the motor 100 is fixed to the rear end portion of the wing shaft 200.

When the wing shaft 200 rotates with the rotation of the rotor 110, the sun gear 410 rotates. When the internal gear 420 is in the fixed state, the planetary gear 430 revolves around the sun gear 410 while rotating along with the rotation of the sun gear 410. The revolving planetary carrier 440 along with the planetary gear 430 rotates, and the roller shaft 300 fixed to the carrier 440 rotates. Since the revolution speed of the planetary gear 430 becomes slower than the rotational speed of the sun gear 410, the drum shaft 300 rotates 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 also becomes larger than the torque transmitted from the drive motor 100 to the wing shaft 200.

A cylindrical bearing portion 510 is provided at a central portion of the bearing unit 500. Rolling shafts 511, 512 are provided at the front and rear portions of the inner portion of the bearing portion 510, and a mechanical seal 513 is provided at the front end portion. Further, on the bearing unit 500, a clutch plate 520 is disposed around the bearing portion 510. As shown in Fig. 5, an annular clutch blade 521 is formed on the clutch piece 520. A serration 522 is formed on the outer peripheral surface of the clutch blade 521. The serrations 522 correspond to the first engaged portion of the present invention. Further, on the bearing unit 500, a fixing flange 530 is formed around the bearing portion 510.

The drum shaft 300 is inserted into the inside of the shaft portion 510. The outer peripheral surface of the drum shaft 300 is supported by the rolling shafts 511, 512. Thereby, the drum shaft 300 can be smoothly rotated in the bearing portion 510. Further, water is prevented from intruding between the shaft portion 510 and the drum shaft 300 by the mechanical seal 513.

The clutch mechanism unit 600 includes a clutch body 610, a plurality of clutch springs 620, and a clutch drive unit 630. The clutch spring 620 and the clutch driving device 630 constitute a moving mechanism portion DM that moves the clutch body 610 in the front-rear direction.

The clutch body 610 has a cylindrical shape. The front surface of the clutch body 610 is fully opened, and the rear surface opens the center portion. As shown in FIG. 6(a), on the rear surface of the clutch body 610, annular rear serrations 612 are formed toward the rear on the outer periphery of the opening portion 611 formed at the center. The rear serrations 612 are formed to be engaged with the serrations 113 by a diameter substantially equal to the serrations 113 of the clutch plates 112. Rear serration 612 It corresponds to the second engaging portion of the present invention. Further, in Fig. 6 (a), the groove portion of the rear serration 612 is painted in gray for convenience.

Further, an annular flange portion 613 is formed at the front end portion of the clutch body 610. As shown in Fig. 6 (b), the front serrations 614 are formed on the inner peripheral surface of the flange portion 613 over the entire circumference. The front serrations 614 are formed to mesh with the serrations 522 of the clutch blades 521 of the bearing unit 500. The front serration 614 corresponds to the first "" joint of the present invention. Further, on the inner peripheral surface of the clutch body 610, guide ribs 615 extending in the front-rear direction are formed at a plurality of positions.

The clutch body 610 is disposed between the bearing unit 500 and the drive motor 100 in such a manner as to enclose the planetary gear mechanism 400. The rear portion of the clutch body 610 is housed inside the drive motor 100. That is, the rear portion of the clutch body 610 coincides with the drive motor 100 in the axial direction of the wing shaft 200 and the drum shaft 300. As shown in Fig. 6(c), the groove portion 421 corresponding to each of the guide ribs 615 is formed on the outer peripheral surface of the inner gear 420, and the guide rib 615 is fitted into the groove portion 421. Thereby, the clutch body 610 is in a state in which the movement in the front-rear direction with respect to the internal gear 420 of the planetary gear mechanism 400 is permitted, and the rotation in the circumferential direction is restricted. A plurality of clutch springs 620 are disposed between the inner side of the rear surface of the clutch body 610 and the support disk 450 of the planetary gear mechanism 400 at substantially equal intervals. The clutch spring 620 corresponds to the elastic member of the present invention.

The clutch driving device 630 includes a driving machine 631 and a pressing lever 632 extending from the driving machine 631 toward the clutch body 610. The driver 631 moves the push lever 632 forward and backward. The push rod 632 corresponds to the pressing member of the present invention.

The drum washing machine 1 performs a washing operation of various operation programs. The washing operation includes a washing process, an intermediate dewatering process, a rinsing process, and a final dewatering process.

In the washing step and the rinsing step, the form of the drive unit 30 can be switched to the first form. In the case of switching to the first form, as shown in Fig. 2, the driver 631 moves the push lever 632 forward. The push lever 632 contacts the flange portion 613 of the clutch body 610 to push the flange portion 613 forward. The clutch body 610 moves forward in opposition to the spring force of the clutch spring 620. Thereby, the front serrations 614 of the clutch body 610 and the serrations 522 of the clutch plates 520 are engaged.

When the front serration 614 is engaged with the serrations 522, the circumferential rotation of the clutch body 610 with respect to the bearing unit 500 is restricted to a non-rotatable state. Thereby, the internal gear 420 of the planetary gear mechanism 400 is in a state of being fixed in a non-rotatable manner. In this state, when the rotor 110 rotates, the wing shaft 200 rotates at a rotation speed equal to the rotation speed of the rotor 110, and the agitating body 24 coupled to the blade shaft 200 also rotates at a rotation speed equal to the rotation speed of the rotor 110. Rotate. Accompanying the wing axis Rotation of 200, the sun gear 410 rotates in the planetary gear mechanism 400. As described above, since the internal gear 420 is in a fixed state, the planetary gear 430 revolves around the sun gear 410 while rotating, and the revolving planetary carrier 440 rotates. Thereby, the drum shaft 300 coupled to the planetary carrier 440 rotates. Since the planetary gear mechanism 400 is decelerated, the drum shaft 300 rotates at a rotation speed slower than the wing shaft 200, and the drum 22 coupled to the drum shaft 300 rotates at a rotation speed slower than that of the agitating body 24. In other words, the agitating body 24 is rotated at a rotational speed faster than the drum 22. Further, the rotation 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, in the outer tank 20, the driving motor 100 alternately performs the right rotation and the left rotation in a state where the water is not in 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. Further, at the rear portion of the drum 22, the laundry comes into contact with the blades 24a of the rotating agitating body 24, and the laundry is rubbed against the blades 24a, or the laundry is stirred 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. In the case of switching to the second mode, as shown in Fig. 3, the driver 631 moves the push lever 632 rearward. The push lever 632 is disengaged from the clutch body 610, and the clutch body 610 is moved rearward by the elastic force of the clutch spring 620. Thereby, the rear serrations 612 of the clutch body 610 and the serrations 113 of the clutch plates 112 are engaged. Further, even in a state where the rear serrations 612 and the serrations 113 are engaged, the clutch spring 620 is maintained in a contracted state, and the elastic clutch body 610 passing through the clutch spring 620 is pressed toward the clutch plates 112. When the rear serrations 612 and the serrations 113 are engaged, the push rods 632 are separated from the clutch body 610.

When the rear serrations 612 and the serrations 113 are engaged, the circumferential rotation of the clutch body 610 with respect to the rotor 110 is restricted, and the clutch body 610 and the rotor 110 are in a rotatable state. In such a state, when the rotor 110 rotates, the wing shaft 200 and the clutch body 610 rotate at a rotation speed equal to the rotation speed of the rotor 110. At this time, in the planetary gear mechanism 400, the sun gear 410 and the internal gear 420 rotate at a rotation speed equal to that of the rotor 110. Thereby, the planetary carrier 440 rotates at a rotation speed equal to that of the rotor 110, and the roller coupled to the carrier 440 The shaft 300 rotates at a rotational speed equal to that of the rotor 110. That is, in the drive unit 30, the wing shaft 200, the clutch body 610, the planetary gear mechanism 400, and the drum shaft 300 are integrally rotated as indicated by a one-dot chain line in FIG. Thereby, the drum 22 and the agitating body 24 are integrally rotated. Further, the clutch spring 620 interposed between the clutch body 610 and the planetary gear mechanism 400 also rotates together with the clutch body 610 and the planetary gear mechanism 400.

In the intermediate dehydration step and the final dehydration step, the rotor 110, i.e., 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 centrifugal force.

As described above, according to the present embodiment, in the washing step and the rinsing step, the drum 22 and the type rotate. Thereby, the laundry in the drum 22 is not only hit by the ablation of the baffle 23 to the inner peripheral surface of the drum 22, but also rubbed or agitated by the blades 24a of the rotating agitating body 24. Therefore, 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 is rotated at a rotation speed equal to that of the drive motor 100, and the agitating body is rotated. The structure in which the drum 22 that requires a larger torque is rotated by decelerating the rotation of the drive motor 100 is used. With this configuration, it is possible to reduce the drive roller 22 and the agitation as compared with the case where the drum 22 is rotated at a rotation speed equal to that of the drive motor 100 and the agitator 24 is rotated by increasing the rotation of the drive motor 100. When the body 24 drives the torque generated by the motor 100, the power consumption of the drive motor 100 can be reduced.

Further, according to the present embodiment, the rotor 110 of the drive motor 100 and the agitating body 24 are coupled by one 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 connected 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. Therefore, assembly of the drive portion becomes easy. In addition, there is no need to worry about the shaft misalignment between the two rotating shafts.

Further, according to the present embodiment, since the speed reduction mechanism that decelerates the rotation of the wing shaft 200 and transmits it to the drum shaft 300 is configured by the planetary gear mechanism 400, the gear constituting the speed reduction mechanism does not pass to the wing shaft 200 and the drum shaft 300. The axial direction of the transmission mechanism portion TR, that is, the size of the drive unit 30 can be reduced. Thereby, since the outer tub 20 and the drum 22 can be enlarged in the front-rear direction, the washing capacity can be increased. Further, according to the present embodiment, in the intermediate dehydration step and the final dehydration step, the clutch mechanism unit 600 switches the form of the drive unit 30 from the first form to the second form, whereby the drum 22 and the agitating body 24 can be provided. The body rotates at high speed. Thereby, the laundry in the drum 22 is not stirred by the rotating body 24, and the dehydration of the laundry can be appropriately performed.

Further, according to the present embodiment, since the clutch mechanism portion 600 is configured to move the tubular clutch body 610 in the front-rear direction on the outer circumference of the internal gear 420, in the axial direction of the wing shaft 200 and the drum shaft 300, The arrangement space of the planetary gear mechanism 400 can be utilized for the movement space of the clutch body 610. Therefore, the size of the drive unit 30 in the axial direction of the wing shaft 200 and the drum shaft 300 can be further reduced.

Further, according to the present embodiment, since the clutch body 610 and the drive motor 100 are overlapped in the axial direction of the wing shaft 200 and the drum shaft 300, the size of the drive unit 30 in the axial direction can be further reduced.

Further, according to the present embodiment, when the clutch body 610 is moved by the elastic force of the clutch spring 620, the rear serrations 612 are engaged with the serrations 113, and when the clutch body 610 and the rotor 110 are rotated by the engagement, The push lever 632 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 lever 632 with the clutch body 610.

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-described embodiment, the speed reduction mechanism that decelerates the rotation of the wing shaft 200 and transmits it to the drum shaft 300 is constituted by the planetary gear mechanism 400. . However, the speed reduction mechanism is not limited to the planetary gear mechanism 400. For example, the speed reduction mechanism may also be constituted by a parallel shaft gear reduction mechanism.

Further, in the above embodiment, by the engagement of the front serrations 614 of the clutch body 610 and the serrations 522 of the clutch plates 520 provided on the bearing unit 500, the circumferential rotation of the clutch body 610 with respect to the bearing unit 500 is limit. Further, by the engagement of the rear serrations 612 of the clutch body 610 and the serrations 113 of the clutch plates 112 provided on the rotor 110, the circumferential rotation of the clutch body 610 with respect to the rotor 110 is restricted. 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 saw teeth, and may have other configurations. For example, it is also possible to employ a structure 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, and the projection is fitted into the recess or the hole. 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 have a structure in which the drum 22 rotates around the horizontal axis.

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

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

Description of the reference numerals

10 housing; 20 outer groove; 22 roller; 24 agitator (rotary body); 24a blade (projection); 30 drive unit (drive); 100 drive motor; 110 rotor; 112 clutch plate; 113 sawtooth (first Two engaged parts); 200 wing shaft (first rotating shaft); 300 drum shaft (second rotating shaft); 400 planetary gear mechanism; 410 sun gear; 420 internal gear; 430 planetary gear; 440 planetary carrier; Bearing unit; 520 clutch plate; 522 sawtooth (first engaged portion); 600 clutch mechanism portion; 610 clutch body; 612 rear serration (second engagement portion); 614 front serration (first engagement portion) 620 Clutch spring (elastic member); 630 clutch drive; 631 drive; 632 push rod (pushing member); TR transmission mechanism; 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;

The rotating body is disposed at a rear portion of the drum so as to rotate coaxially with the drum, and has a projecting portion that contacts the laundry on the surface; and the rotating portion is faster than the rotating speed of the drum.

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

The drive unit is disposed behind the outer tub and includes a drive motor and a transmission mechanism that transmits torque generated by the drive motor to the rotating body and the drum.

The transmission mechanism portion includes:

a first rotating shaft that rotates due to a torque of the driving motor and transmits the rotation to the rotating body; and a speed reducing mechanism that decelerates rotation of the first rotating shaft;

The second rotating shaft rotates coaxially with the first rotating shaft at a rotational speed decelerated by the speed reducing mechanism, and transmits the rotation to the drum.

3. The drum washing machine according to claim 2, wherein the rotors are coupled,

The speed reduction mechanism includes a planetary gear mechanism having: a sun gear; an annular internal gear surrounding the sun gear; a plurality of planetary gears meshing with both the sun gear and the internal gear, and Rotating around the sun gear; and the planet carrier rotating with the revolution of the planet gears, the sun gear being disposed on the first rotating shaft

The second rotating shaft encloses the first rotating shaft, the front end portion is coupled to the drum, and the rear end portion is coupled to the planetary carrier.

4. The drum washing machine according to claim 3, wherein

The driving portion further includes a clutch mechanism portion,

The clutch mechanism unit cuts the shape of the driving portion between the first form and the second form In the first aspect, the internal gear is fixed so as not to be rotatable, thereby enabling the first rotating shaft to rotate at a rotational speed equal to the rotational speed of the rotor, and to cause the second rotation The shaft rotates at a rotational speed decelerated by the planetary gear mechanism, and the second form rotates the internal gear together with the rotor, thereby enabling the first rotating shaft, the second rotating shaft, and the The planetary gear mechanism integrally rotates at a rotational speed equal to the rotational speed of the rotor.

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

The driving portion further includes a bearing unit that rotatably supports the second rotating shaft, the clutch mechanism portion including: a cylindrical clutch body surrounding an outer circumference of the internal gear, with respect to the internal gear The movement in the front-rear direction is allowed and the rotation in the circumferential direction is restricted; and the moving mechanism portion moves the clutch body in the forward and backward directions,

a first "" joint portion and a second engaging portion are respectively disposed at a front end portion and a rear end portion of the clutch body, and a first engaged portion is respectively disposed at the bearing unit and the rotor And the second engaged portion,

a circumferential direction of the clutch body with respect to the bearing unit when the clutch body is moved forward by the moving mechanism portion to engage the first engaging portion with the first engaged portion The rotation is restricted, the internal gear is fixed so as not to rotate,

Rotation of the clutch body with respect to the circumferential direction of the rotor when the clutch body is moved rearward by the moving mechanism portion to engage the second engaging portion with the second engaged portion Limited, the internal gear can rotate with the rotor.

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

The clutch body is disposed between the bearing unit and the drive motor such that a rear portion of the clutch body is housed inside the drive motor.

The drum washing machine according to claim 5 or 6, wherein

The moving mechanism portion includes:

An elastic member interposed between the clutch body and the planetary gear mechanism to move the clutch body rearward by an elastic force to engage the second engaging portion with the second engaged portion; And the pressing member, the clutch body is moved forward by pushing the clutch body, the first engaging portion is engaged with the first engaged portion, and the second engaging portion is engaged The portion is separated from the clutch body in a state of being engaged with the second engaged portion.