JP6397216B2 - Drum washing machine - Google Patents

Description

  The present invention relates to a drum type washing machine. Such a drum-type washing machine may be one that performs continuously from washing to drying, or one that performs washing but does not dry.

  Conventionally, a drum-type washing machine rotates a horizontal axis drum in an outer tub with water stored in the bottom, lifts and drops the laundry by a baffle provided in the drum, and the laundry is moved to the inner periphery of the drum. Laundry is performed by hitting the surface (see Patent Document 1).

  As described above, in the configuration in which the laundry is stirred by the baffle, the laundry is unlikely to be entangled or rubbed with each other. For this reason, the drum-type washing machine tends to have a smaller mechanical force acting on the laundry and lower the washing performance than a fully automatic washing machine that rotates the pulsator in the washing and dewatering tub to wash the laundry.

  Therefore, in the drum type washing machine, in order to improve the cleaning performance, a configuration 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 rotational speeds when it is easy to wash can be adopted.

JP 2013-240577 A

  When realizing a drum-type washing machine that rotates the drum and the stirrer at different rotational speeds, the drive unit that drives the drum and the stirrer tends to increase in size due to the addition of a speed reduction mechanism and the like, resulting in an increase in the number of components . Therefore, in order to suppress a decrease in the size of the outer tub and the drum and to secure as much washing capacity as possible, it is necessary to suppress an increase in the size of the drive unit.

  This invention is made | formed in view of this subject, and it aims at providing the drum type washing machine which can suppress the increase in the size of a drive part, aiming at the improvement of washing | cleaning performance.

  A drum-type washing machine according to a main aspect of the present invention includes an outer tub disposed in a housing, a drum disposed in the outer tub and rotatable about a horizontal axis or an inclined axis inclined with respect to a horizontal direction. A baffle provided on an inner peripheral surface of the drum; a rotating body disposed on a rear portion of the drum and having a protruding portion that comes into contact with laundry; and the drum and the rotating body are rotated by the rotating body. And a drive section that rotates so that the speed is higher than the rotation speed of the drum. The drive unit includes a drive motor, a first rotating shaft that is coupled to the rotating body and transmits torque of the drive motor to the rotating body, and a speed change mechanism that shifts the rotation of the rotor of the drive motor; A first bearing connected to the drum and transmitting torque of the drive motor to the drum; and a second rotating shaft including the first rotating shaft and the speed change mechanism; and a first bearing disposed so as to sandwich the speed change mechanism; A bearing unit having a second bearing and rotatably supporting the second rotating shaft 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 the first shaft portion and the second shaft portion. And an accommodating portion that bulges outward and accommodates the speed change mechanism. Further, the bearing unit includes a first unit including the first bearing and a second unit including the second bearing, and the first unit and the second unit are arranged in an axial direction of the second rotating shaft. , And coupled from both sides of the housing part.

  According to the above configuration, since the space generated between the first bearing and the second bearing is used as a space for arranging the speed reduction mechanism in order to favorably support the load by the drum with the second rotating shaft, The size of the drive unit can be reduced in the axial direction of the rotation shaft. Thereby, since an outer tub and a drum can be enlarged in the front-back direction, washing capacity can be increased.

  In addition, according to the above configuration, the second rotary shaft is inserted because the second rotary shaft containing the speed change mechanism can be accommodated in the bearing unit by coupling the first unit and the second unit. In order to secure the opening, it is not necessary to use the first bearing or the second bearing having a larger outer shape than necessary, or to increase the thickness of the first shaft portion or the second shaft portion more than necessary.

  In the drum type washing machine according to this aspect, the first unit has a first peripheral surface having a circular shape or a circular arc shape concentric with the first bearing, and the second unit is configured with the second bearing. It can be set as the structure which has the 2nd surrounding surface which has concentric circular shape or circular arc shape. In this case, the first unit and the second unit are coupled by a spigot fitting between the first peripheral surface and the second peripheral surface.

  According to the above configuration, even when the bearing unit is configured to be divided, the center of the first bearing and the center of the second bearing can be matched with high accuracy. For this reason, it can prevent that a 2nd rotating shaft cannot rotate smoothly by the axial shift of the center of a 1st bearing, and a 2nd bearing.

  In the drum type washing machine according to this aspect, the bearing unit is configured such that the second unit is positioned on the drive motor side and a fixing portion for fixing the stator of the motor is provided on the second unit. Can be.

  According to said structure, since a stator is fixed to the 2nd unit in which a 2nd bearing is provided, the center of the rotor concentric with a 2nd bearing and the center of a stator can be made to correspond with a sufficient precision. Thereby, since the clearance gap between a rotor and a stator can be kept constant, a drive motor can be rotated stably.

  In the drum type washing machine according to this aspect, the speed change mechanism may include a speed reduction mechanism that decelerates the rotation of the rotor. In this case, the speed reduction mechanism includes a sun gear that rotates as the rotor of the drive motor rotates, an annular internal gear that surrounds the sun gear, and a plurality of interposed gears between the sun gear and the internal gear. It has a planetary gear and a planet carrier that rotatably holds these planetary gears. The second rotation shaft is fixed to the internal gear and rotates as the internal gear rotates. The planetary carrier includes a shaft portion that is coaxial with the second rotation shaft and has a tip portion protruding from the second rotation shaft toward the rotor. The drive unit further includes a clutch mechanism unit. The clutch mechanism portion is provided so as to be related to a tip portion of the shaft portion protruding from the second rotation shaft, and the shaft portion cannot be rotated so that the first rotation shaft and the second rotation shaft are moved. A first mode in which the rotation speed of the second rotation shaft is made slower than the rotation speed of the first rotation shaft in accordance with a reduction ratio by the speed change mechanism, and the shaft portion rotates with the rotor. Thus, the form of the drive unit is switched between a second form in which the first rotating shaft, the speed reduction mechanism, and the second rotating shaft are integrally rotated at a rotational speed equal to the rotational speed of the rotor.

  According to said structure, while connecting a 2nd rotating shaft to an internal gear, the front-end | tip part of the axial part provided in the planetary carrier protrudes outside a 2nd rotating shaft, and a clutch mechanism part concerns on the protruded front-end | tip part. Thus, 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. Therefore, even if the speed reduction mechanism is configured to be sandwiched between the first bearing and the second bearing, the speed reduction mechanism is included in the second rotating shaft. Can be satisfactorily switched between. In addition, by adjusting the number of teeth of the sun gear and the internal gear, the reduction ratio between the rotor and the second rotating shaft can be set, and a wide range of reduction ratios can be set.

  In the case of the above configuration, the clutch mechanism portion is further fitted into the tip portion, the shaft portion is allowed to move in the axial direction with respect to the tip portion, and the shaft portion is moved in the circumferential direction. The clutch body that is restricted from rotating and the moving mechanism that moves the clutch body in the axial direction may be included. In this case, a first engagement portion and a second engagement portion are provided at the end on the bearing unit side and the end on the rotor side of the clutch body, respectively. The second unit located on the drive motor side is provided with a first engaged portion, and the rotor is provided with a second engaged portion. When the clutch body is moved to the second unit side by the moving mechanism and the first engaging portion is engaged with the first engaged portion, the clutch body rotates in the circumferential direction with respect to the second unit. When the movement is restricted and the shaft portion cannot rotate, the clutch body is moved to the rotor side by the moving mechanism portion, and the second engaging portion is engaged with the second engaged portion, The rotation of the clutch body in the circumferential direction with respect to the rotor is restricted, and the shaft portion can be rotated together with the rotor.

  With such a configuration, it is possible to specifically realize the clutch mechanism that switches the form of the drive part between the first form and the second form by being related to the shaft part, that is, the planet carrier. . In addition, since the first engaged portion that engages with the first engagement portion of the clutch body is formed in the second unit in which the second bearing that is concentric with the shaft portion into which the clutch body is fitted is formed. The center of one engaging part and the center of a 1st to-be-engaged part can be engaged accurately.

  In the case of the above configuration, the moving mechanism unit is further interposed between the clutch body and the bearing unit, and moves the clutch body to the rotor side by an elastic force, so that the second engagement is performed. An elastic member that engages the second engagement portion with the second engagement portion, and the clutch body is moved to the bearing unit side by pushing the clutch body, and the first engagement portion is moved to the first engagement portion. A pressing member that is in contact with the clutch body in a state of being engaged with the portion, and is separated from the clutch body in a state of being engaged with the second engaged portion of the second engagement portion.

  With such a configuration, the clutch body is moved by the elastic force of the elastic member, whereby the second engaging portion is engaged with the second engaged portion, and the clutch body is rotated together with the rotor by the engagement. When doing so, the pressing member is separated from the clutch body. For this reason, the rotation of the rotor and the clutch body is not hindered by the contact of the pressing member with the clutch body.

  ADVANTAGE OF THE INVENTION According to this invention, the drum-type washing machine which can suppress the increase in the size of a drive part can be provided, improving a cleaning performance.

  The effects and significance of the present invention will become more apparent from the following description of embodiments. However, the following embodiment is merely an example when the present invention is implemented, and the present invention is not limited to what is described in the following embodiment.

It is side surface sectional drawing which shows the structure of the drum type washing machine based on embodiment. It is sectional drawing which shows the structure of the drive unit based on embodiment. It is a front view of the rotor which shows the structure of the rotor of the drive motor based on Embodiment. It is a figure which shows the structure of the blade axis | shaft, drum axis | shaft, and planetary gear mechanism which concern on embodiment. It is a figure which shows the structure of the front part unit of a bearing unit based on Embodiment. It is a figure which shows the structure of the rear part unit of the bearing unit based on embodiment. It is a figure which shows the structure of the rear part unit of the bearing unit based on embodiment. It is a figure which shows the structure of the clutch body of a clutch mechanism part based on embodiment. It is a figure which shows the structure of the moving mechanism part of a clutch mechanism part based on embodiment. It is a figure for demonstrating operation | movement of the clutch mechanism part based on Embodiment. It is a figure for demonstrating operation | movement of a drive unit, a drum, and a stirring body in the washing | cleaning process and the rinse process based on Embodiment. It is a figure for demonstrating operation | movement of a drive unit, a drum, and a stirring body in the intermediate | middle dehydration process and the final dehydration process based on Embodiment. It is a figure which shows the structure of the drive unit compared with embodiment.

  Hereinafter, a drum type washing machine having no drying function according to an embodiment of the drum type washing machine of the present invention will be described with reference to the drawings.

  FIG. 1 is a side sectional view showing the configuration of the drum type washing machine 1.

  The drum-type washing machine 1 includes a housing 10 that forms an appearance. The front surface 10a of the housing 10 is inclined from the central portion to the upper portion, and the laundry inlet 11 is formed on the inclined surface. The insertion port 11 is covered with a door 12 that can be freely opened and closed.

  The outer tub 20 is elastically supported by a plurality of dampers 21 in the housing 10. A drum 22 is rotatably disposed in the outer tub 20. The outer tub 20 and the drum 22 are inclined with respect to the horizontal direction so that the rear surface side becomes lower. As a result, the drum 22 rotates around the tilt axis tilted with respect to the horizontal direction. The inclination angle of the outer tub 20 and the drum 22 can be about 10 to 20 degrees. The opening 20a on the front surface of the outer tub 20 and the opening 22a on the front surface of the drum 22 are opposed to the charging port 11, and both the charging port 11 is closed by the door 12. A large number of dewatering holes 22 b are formed on the inner peripheral surface of the drum 22. Further, three baffles 23 are provided on the inner peripheral surface of the drum 22 at substantially equal intervals in the circumferential direction.

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

  A drive unit 30 that generates torque for driving the drum 22 and the stirring 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 stirring 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 rotation speed at which the centrifugal force applied to the laundry in the drum 22 is smaller than gravity, and the stirring member 24 is faster than the rotation speed of the drum 22. Rotate with On the other hand, during the dehydration process, the drive unit 30 integrally rotates the drum 22 and the stirring body 24 at a rotational speed at which the centrifugal force applied to the laundry in the drum 22 is much greater than gravity. The detailed configuration of the drive unit 30 will be described later.

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

  A detergent box 50 is disposed in the upper front portion of the housing 10. In the detergent box 50, a detergent container 50a in which detergent is accommodated is accommodated so that it can be pulled out from the front. The detergent box 50 is connected by a water supply hose 52 to a water supply valve 51 disposed at the upper rear part in the housing 10. The detergent box 50 is connected to the upper part of the outer tub 20 by a water injection pipe 53. When the water supply valve 51 is opened, tap water is supplied from the water tap into the outer tub 20 through the water supply hose 52, the detergent box 50 and the water injection pipe 53. At this time, the detergent accommodated in the detergent container 50 a flows into the water and is supplied into the outer tub 20.

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

  FIG. 2 is a cross-sectional view showing the configuration of the drive unit 30. FIG. 3 is a front view of the rotor 110 showing the configuration of the rotor 110 of the drive motor 100. FIGS. 4A and 4B are diagrams showing the configuration of the blade shaft 200, the drum shaft 300, and the planetary gear mechanism 400. 4A is a side cross-sectional view, and FIG. 4B is a cross-sectional view taken along the line AA ′ of FIG. 4A. FIGS. 5A and 5B are views showing the configuration of the front unit 510 of the bearing unit 500, and are a front view and a rear view of the front unit 510, respectively. 6 and 7 are diagrams showing a configuration of the rear unit 520 of the bearing unit 500. FIG. FIG. 6 is a front view of the rear unit 520. FIG. 7A is a rear view of the rear unit 520, and FIG. 7B is an enlarged perspective view of the rear part of the rear unit 520. 8A to 8C are views showing the configuration of the clutch body 610 of the clutch mechanism portion 600, and are a front view, a right side view, and a rear view of the clutch body 610, respectively. FIGS. 9A to 9C are views showing the configuration of the moving mechanism part DM of the clutch mechanism part 600, and are a rear view, a right side view, and a top view of the moving mechanism part DM, respectively. FIGS. 10A and 10B are diagrams for explaining the operation of the clutch mechanism 600. FIG. 8A to 8C show a state where the clutch body 610 is mounted on the carrier shaft 442 of the planet carrier 440.

  The drive unit 30 includes a drive motor 100, a blade shaft 200, a drum shaft 300, a planetary gear mechanism 400, a bearing unit 500, and a clutch mechanism unit 600. The drive motor 100 generates torque for driving the stirrer 24 and the drum 22. The blade shaft 200 is rotated by the torque of the drive motor 100 and transmits the rotation to the stirring body 24. The blade axis 200 corresponds to the first rotating shaft of the present invention. The planetary gear mechanism 400 decelerates the rotation of the blade shaft 200, that is, 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 speed change mechanism and the speed reduction mechanism of the present invention. The drum shaft 300 rotates coaxially with the blade shaft 200 at a rotational speed reduced 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 rotatably supports the blade shaft 200 and the drum shaft 300. The clutch mechanism 600 rotates the agitator 24, that is, the blade shaft 200 at a rotational speed equal to the rotational speed of the drive motor 100, and the drum 22, that is, the drum shaft 300, at a rotational speed reduced by the planetary gear mechanism 400. The first form that can be rotated and the agitator 24 and the drum 22, that is, the blade shaft 200, the drum shaft 300, and the planetary gear mechanism 400 can be integrally rotated at a rotational speed equal to that of the drive motor 100. The form of the drive unit 30 is switched between the second form.

  Referring to FIGS. 2 and 3, 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 permanent magnets 111 are arranged on the entire inner circumferential surface thereof. As shown in FIG. 3, a circular boss 112 is formed at the center of the rotor 110. A boss hole 113 for fixing the blade shaft 200 is formed in the boss part 112, and an annular engaged recess 114 is formed on the outer periphery of the boss hole 113. The outer peripheral part of the engaged recessed part 114 has the uneven | corrugated | grooved part 114a over the perimeter. The engaged recess 114 corresponds to the second engaged portion of the present invention.

  The stator 120 has a winding 121 on the outer periphery. When a drive current is supplied to the winding 121 of the stator 120 from a control circuit (not shown), the rotor 110 rotates. Screw holes 122 are formed at intervals of approximately 120 degrees on the top and left and right of the stator 120. Each screw hole 122 has the same distance in the radial direction from the center of the stator 120. In FIG. 2, only the upper screw hole 122 is shown.

  Referring to FIGS. 2 and 4, drum shaft 300 has a hollow shape and includes blade axis 200 and planetary gear mechanism 400. The drum shaft 300 is provided between the front shaft portion 300a, the rear shaft portion 300b, and the front shaft portion 300a and the rear shaft portion 300b, and is accommodated to bulge outward from the front shaft portion 300a and the rear shaft portion 300b. Part 300c. The front 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 accommodated in the accommodating portion 300c. The front shaft portion 300a is formed so that the front portion has a larger inner diameter than the rear portion, and the first sliding bearing 301 is disposed in the large diameter portion 300d having a larger inner diameter. Similarly, a mechanical seal 302 is disposed in the large-diameter portion 300d in front of the first slide bearing 301 with a regulation ring described later interposed therebetween. The first plain bearing 301 and the mechanical seal 302 are inserted into the large diameter portion 300d from the front, and are fixed to the drum shaft 300 by a fixing method such as press fitting. The drum shaft 300 is divided in the front-rear direction so that the planetary gear mechanism 400 can be accommodated in the accommodating portion 300c, and is configured by two members, that is, the front member M1 and the rear member M2.

  The planetary gear mechanism 400 includes a sun gear 410, an annular internal gear 420 surrounding the sun gear 410, a plurality of planetary gears 430 interposed between the sun gear 410 and the internal gear 420, and the planetary gears 430. And a planet carrier 440 that is rotatably held by a shaft 441.

  The set of planetary gears 430 includes 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, 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 inside thereof is formed hollow because the blade shaft 200 is inserted. The carrier shaft 442 is formed so that the inner diameter of the part extending from the tip part to the base part is larger than the base part, and the second slide bearing 443 is disposed in the large diameter part 442a having a larger inner diameter. A spline 442c is formed on the outer peripheral surface of the front end portion 442b of the carrier shaft 442 protruding rearward from the drum shaft 300.

  An annular regulating flange 201 is formed at the rear end of the blade shaft 200. The blade shaft 200 is inserted into the drum shaft 300 from the rear. An annular regulating ring 202 is fixed to the front end portion of the inserted blade axis 200. Like the first slide bearing 301 and the mechanical seal 302, the restriction ring 202 is inserted into the large diameter portion 300d from the front, and is fixed to the blade shaft 200 by a fixing method such as press fitting. The regulating ring 202 is in contact with the first plain 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 engages with the rear end of the carrier shaft 442 and the restricting ring 202 engages with the first slide bearing 301 via the first washer 203, whereby the blade shaft 200 restricts movement in the front-rear direction. Is done.

  The outer peripheral surface of the blade shaft 200 inserted into the drum shaft 300 slides between the first slide bearing 301 and the second slide bearing 443. Thereby, the blade shaft 200 rotates smoothly in the drum shaft 300. Further, the mechanical seal 302 prevents water from entering between the drum shaft 300 and the blade shaft 200. Further, when the blade shaft 200 rotates, the restriction ring 202 slides between the first washer 203 and the second washer 204. For this reason, the wear of the first slide bearing 301 and the mechanical seal 302 caused by sliding of the regulating ring 202 is prevented.

  As described above, the first slide bearing 301, the regulating ring 202, and the mechanical seal 302 can all be arranged in the large-diameter portion 300d by being inserted from the front, so that the assemblability can be improved.

  A sun gear 410 is fixed to a middle part of the blade axis 200. As shown in FIG. 4B, a key portion 421 extending in the front-rear direction is formed at a plurality of locations on the outer peripheral surface of the internal gear 420, and the inner peripheral surface of the drum shaft 300 corresponds to the key portion 421. A key groove portion 303 is formed. When the key portion 421 and the key groove portion 303 are engaged, the drum shaft 300 and the internal gear 420 are fixed in the circumferential direction. Further, the rear end portion of the blade shaft 200 protrudes rearward from the carrier shaft 442 and is fixed to the boss hole 113 of the rotor 110.

  When the blade shaft 200 rotates with the rotation of the rotor 110, the sun gear 410 rotates. When the planetary carrier 440 is fixed so as not to rotate, the planetary gear 430 cannot revolve, so the sun gear 410 rotates only with 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. As the second gear 432 rotates, the internal gear 420 rotates in the same direction as the second gear 432, that is, in the same direction as the sun gear 410. As a result, the drum shaft 300 fixed to the internal gear 420 rotates. The rotation directions of the gears 410, 420, 431, 432 and the drum shaft 300 are indicated by arrows in FIG.

  Since the rotational speed of the internal gear 420 is slower than the rotational speed of the sun gear 410, the drum shaft 300 rotates at a lower rotational speed than the blade shaft 200. Thus, since the rotational speed of the blade shaft 200 is reduced and transmitted to the drum shaft 300, the torque transmitted to the drum shaft 300 is larger than the torque transmitted from the drive motor 100 to the blade shaft 200.

  With reference to FIGS. 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.

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

  On the outer periphery of the front unit 510, mounting holes 515 are formed at four locations on the top, bottom, left, and right. Further, two mounting bosses 516 are formed at the lower portion of the outer peripheral portion of the front unit 510. A mounting hole 516 a is formed in the mounting boss 516.

  A cylindrical cover 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 surface side at the center portion of the rear unit 520. Behind 521, a cylindrical rear bearing portion 522 having an inner diameter smaller than the outer diameter of the accommodating portion 300c is provided. In the rear bearing portion 522, a second rolling bearing 523 is disposed on the front side, and a spring receiving plate 524 is provided behind the second rolling bearing 523. The second rolling bearing 523 corresponds to the second bearing of the present invention. A spline 525 is formed on the inner surface of the rear end portion of the rear bearing portion 522 over the entire circumference. The spline 525 corresponds to the first engaged portion of the present invention.

  The rear unit 520 is formed with three mounting bosses 526 on the rear surface side. Each mounting boss 526 is formed at three positions on the upper and left and right sides corresponding to the screw holes 122 of the stator 120. A mounting hole 526 a is formed in the mounting boss 526. Each mounting hole 526a has the same distance in the radial direction from the center P2 of the second rolling bearing 523 in a state of being disposed in the rear bearing portion 522. The mounting boss 526 corresponds to the fixing portion of the present invention.

  An annular fitting rib 527 is formed on the front side at the center of the rear unit 520. The outer peripheral surface 527a of the fitting rib 527 has a circular shape, and the center of the circle 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 recessed portion 514 to be fitted. The outer peripheral surface 527a of the fitting rib 527 corresponds to the second peripheral surface of the present invention.

  A screw hole 528 is formed on the outer periphery of the rear unit 520. Each screw hole 528 is formed at four positions on the top, bottom, left, and right corresponding to the mounting hole 515 of the front unit 510.

  The front unit 510 and the rear unit 520 are coupled together with the drum shaft 300 including the blade shaft 200 and the planetary gear mechanism 400 set in 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. As described above, the front unit 510 and the rear unit 520 are coupled by inlay fitting between the outer peripheral surface 527a of the fitting rib 527 and the outer peripheral surface 514a of the fitted recess 514. The screw 530 passes through the screw hole 528 and is fixed to the mounting hole 515. Thereby, the front unit 510 and the rear unit 520 are fixed. In this way, the drum shaft 300 is arranged inside the bearing unit 500.

  The planetary gear mechanism 400 is accommodated in the accommodating portion 300c of the drum shaft 300, and is arranged in a space generated between the first rolling bearing 513 and the second rolling bearing 523. Here, in order to satisfactorily support the load due to the heavy drum 22 by the drum shaft 300, in the bearing unit 500, it is necessary to provide a certain distance between the first rolling bearing 513 and the second rolling bearing 523. In the present embodiment, the space generated between the first rolling bearing 513 and the second rolling bearing 523 is used as an arrangement space for the planetary gear mechanism 400, so that the two rolling bearings 513 and 523 are arranged behind the two rolling bearings 513 and 523. Compared with the configuration in which the planetary gear mechanism 400 is disposed, the size of the drive unit 30 can be reduced in the axial direction of the drum shaft 300.

  In the drum shaft 300, the outer peripheral surface of the front shaft portion 300 a is received by the first rolling bearing 513, and the rear shaft portion 300 b is received by the second rolling bearing 523. As a result, the drum shaft 300 rotates smoothly in the bearing unit 500. Further, the mechanical seal 512 is provided at the front end portion of the front bearing portion 511, thereby preventing 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 passes through the screw hole 122 and is fixed to the mounting hole 526a.

  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 drive unit 30 is mounted on the outer tub 20, the blade 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 stirring body 24 is fixed to the blade shaft 200.

  Referring to FIGS. 8 to 10, clutch mechanism unit 600 includes a clutch body 610, a clutch spring 620, a clutch lever 630, a lever support 640, a clutch drive device 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 unit DM that moves the clutch body 610 in the front-rear direction.

  The clutch body 610 has a substantially disk shape. An annular spline 611 is formed on the outer peripheral surface of the front end portion of the clutch body 610. The spline 611 is formed to engage with the spline 525 at the rear end of the rear unit 520. The spline 611 corresponds to the first engagement portion of the present invention. A flange portion 612 is formed on the outer peripheral surface of the clutch body 610 behind the spline 611. Further, the clutch body 610 is formed with an annular engagement flange portion 613 at the rear end. The engaging flange portion 613 has the same shape as the engaged recessed portion 114 of the rotor 110, and has an uneven portion 613a on the entire outer periphery. When the engaging flange portion 613 is inserted into the engaged concave portion 114, the concave and convex portions 613a and 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 in the center of the front surface of the clutch body 610. A spline 614 a is formed on the inner peripheral surface of the shaft hole 614. The spline 614 a is engaged with the spline 442 c of the carrier shaft 442. As a result, the clutch body 610 is allowed to move in the front-rear direction with respect to the carrier shaft 442 and is restricted from rotating in the circumferential direction. In addition, an annular housing groove 615 is formed outside the shaft hole 614 on the front surface of the clutch body 610. The accommodation groove 615 has a depth reaching the rear end. As shown in FIG. 2, a clutch spring 620 is accommodated in the accommodation groove 615. The clutch spring 620 corresponds to the elastic member of the present invention. The clutch spring 620 has one end in contact with the spring receiving plate 524 of the rear unit 520 and the other end in contact with the bottom surface of the receiving groove 615.

  The clutch lever 630 includes a substantially semicircular upper lever 631 that extends along the outer peripheral surface of the lower half of the clutch body 610, and a lower lever 632 that extends downward from the lowermost portion of the upper lever 631. At the upper left and right end portions of the upper lever 631, a pressing portion 633 that contacts the rear surface 612 a of the flange portion 612 of the clutch body 610 and pushes the flange portion 612 forward is formed. The pressing part 633 corresponds to the pressing member of the present invention. In FIG. 9C, the clutch body 610 is drawn for convenience of explanation.

  A support shaft 634 is fixed to the clutch lever 630. The support shaft 634 penetrates the left and right sides of the clutch lever 630, and both end portions thereof protrude from the clutch lever 630 to the left and right.

  The lever support 640 supports the clutch lever 630 in a freely rotatable manner. The lever support 640 includes a bottom plate 641 and arm pieces 642 that rise from both ends of the bottom plate 641. A support shaft hole 643 is formed in the arm piece 642. The support shaft 634 is passed through the support shaft hole 643. Thereby, the clutch lever 630 can be rotated in the front-rear direction around the support shaft 634.

  A spring 644 is interposed between the clutch lever 630 and the lever support 640. One end of the spring 644 is fixed to the mounting shaft 645 of the lever support 640, and the other end is passed through the insertion hole 635 provided in the clutch lever 630, and the attachment provided in the clutch lever 630 is the same as the insertion hole 635. Fixed to the shaft 636. In the assembled state of the clutch mechanism 600, the spring 644 is in an extended state, and the clutch lever 630 is pulled in the direction in which the lower end of the lower lever 632 moves forward by the elastic force of the spring 644.

  Clutch drive device 650 includes a torque motor 651 and a disc-shaped cam 652 that rotates around the horizontal axis by the torque of torque motor 651. The upper surface of the cam 652 contacts the lower end of the lower lever 632. The upper surface of the cam 652 has a first contact surface 652a with a high height provided on one end side, a second contact surface 652b with a low height provided on the other end side, and a first contact surface 652a and a second contact. And an inclined surface 652c connecting the surface 652b.

  The lever support 640 and the clutch driving device 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 with screws.

  When the form of the drive unit 30 is switched from the second form to the first form, as shown in FIG. 10A, the first contact surface 652a is positioned upward by the torque motor 651, and the second contact surface 652b. The cam 652 is rotated so that is positioned below. As the cam 652 rotates, the lower end of the lower lever 632 is sequentially pushed by the inclined surface 652c and the first contact surface 652a to move backward. 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 lever 631 pushes the flange portion 612 of the clutch body 610 forward, and the clutch body 610 moves forward against the elastic force of the clutch spring 620.

  On the other hand, when the form of the drive unit 30 is switched from the first form to the second form, the second contact surface 652b is positioned upward by the torque motor 651 as shown in FIG. The cam 652 is rotated so that the surface 652a is positioned below. As the cam 652 rotates, the lower end of the lower lever 632 moves forward along the inclined surface 652c and the second contact surface 652b by the elastic force of the spring 644. The clutch lever 630 rotates rearward about the support shaft 634, and the upper lever 631 moves rearward. The pressing portion 633 of the upper lever 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.

  The drum type washing machine 1 performs a washing operation of various operation courses. The washing operation includes a washing process, an intermediate dehydration process, a rinsing process, and a final dehydration process.

  FIGS. 11A and 11B are diagrams for explaining operations of the drive unit 30, the drum 22, and the stirring member 24 in the washing process and the rinsing process. FIGS. 12A and 12B are diagrams for explaining operations of the drive unit 30, the drum 22, and the stirring body 24 in the intermediate dehydration process and the final dehydration process.

  In the washing process and the rinsing process, the form of the drive unit 30 is switched to the first form. When the clutch body 610 moves forward as shown in FIG. 10A by switching to the first form, the spline 611 of the clutch body 610 and the spline 525 of the bearing unit 500 are shown in FIG. 11A. And engage. Accordingly, the clutch body 610 is restricted from rotating in the circumferential direction with respect to the bearing unit 500 and cannot rotate, so that the carrier shaft 442 of the planetary gear mechanism 400, that is, the planet carrier 440 cannot be rotated. It becomes a fixed state. In such a state, when the rotor 110 rotates, the blade shaft 200 rotates at a rotation speed equal to the rotation speed of the rotor 110, and the stirring body 24 connected to the blade shaft 200 also rotates at a rotation speed equal to the rotation speed of the rotor 110. Rotate with. As the blade shaft 200 rotates, the sun gear 410 rotates in the planetary gear mechanism 400. As described above, since the planet 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 the opposite direction to the sun gear 410, respectively, and the internal gear 420 It rotates in the same direction as the sun gear 410. As a result, the drum shaft 300 fixed to the internal gear 420 rotates. Since the speed is reduced by the planetary gear mechanism 400, the drum shaft 300 rotates in the same direction as the blade shaft 200 at a lower rotational speed than the blade shaft 200, and the drum 22 fixed to the drum shaft 300 is more than the stirring body 24. It rotates in the same direction as the stirring member 24 at a low rotational speed. In other words, the stirring member 24 rotates in the same direction as the drum 22 at a rotational speed faster than that of the drum 22. The rotational speed of the rotor 110 and the reduction ratio by the planetary gear mechanism 400 are such that the agitator 24 rotates at a rotational speed at which the laundry can be rubbed and stirred to an extent that does not hurt, and the rotational speed of the drum 22 is The centrifugal force acting on the laundry in 22 is appropriately set so that the rotational speed becomes smaller than the gravity.

  In the washing step and the rinsing step, the drive motor 100 alternately rotates clockwise and counterclockwise in a state where water is accumulated in the outer tub 20 up to a predetermined water level that does not reach the lower edge of the inlet 11. As a result, the drum 22 and the stirring body 24 alternately rotate clockwise and counterclockwise while the rotation speed of the stirring body 24 is faster than the rotation speed of the drum 22. The laundry in the drum 22 is beaten against the inner peripheral surface of the drum 22 by being scraped and dropped by the baffle 23. In addition, at the rear part of the drum 22, the laundry comes into contact with the blades 24a of the rotating stirring body 24, and the laundry is rubbed against the blades 24a or the laundry is stirred by the blades 24a. As a result, the laundry is washed or rinsed.

  Next, in the intermediate dehydration process and the final dehydration process, the form of the drive unit 30 is switched to the second form. When the clutch body 610 moves rearward as shown in FIG. 10B by switching to the second configuration, the engagement flange portion 613 of the clutch body 610 moves to the position of the rotor 110 as shown in FIG. The concave and convex portions 613a of the engaging flange portion 613 and the concave and convex portions 114a of the concave portion 114 to be engaged are engaged with each other. Even when the engagement flange portion 613 is fitted in the engaged recess 114, the clutch spring 620 is kept in a contracted state, and the engagement flange portion 613 is caused to move by the elastic force of the clutch spring 620. Pressed against the engaging recess 114. When the engaging flange portion 613 and the engaged recessed portion 114 are engaged, the pressing portion 633 is in a state separated from the clutch body 610.

  When the engagement flange portion 613 and the engaged recess 114 are engaged, the rotation of the clutch body 610 in the circumferential direction with respect to the rotor 110 is restricted, and the clutch body 610 becomes rotatable with the rotor 110. In such a state, when the rotor 110 rotates, the blade shaft 200 and the clutch body 610 rotate at a rotational speed equal to the rotational speed of the rotor 110. At this time, in the planetary gear mechanism 400, the sun gear 410 and the planet carrier 440 rotate at the same rotational speed as the rotor 110. As a result, the internal gear 420 rotates at the same rotational speed as the sun gear 410 and the planet 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 a one-dot chain line in FIGS. 12A and 12B, the blade shaft 200, the planetary gear mechanism 400, and the drum shaft 300 rotate together. Thereby, the drum 22 and the stirring body 24 rotate integrally. The clutch spring 620 also rotates together with the clutch body 610.

  In the intermediate dewatering process and the final dewatering process, the rotor 110, that is, the drum 22 and the stirring body 24 rotate at a rotation speed at which the centrifugal force acting on the laundry in the drum 22 is much larger than the gravity. By the action of centrifugal force, the laundry is pressed against the inner peripheral surface of the drum 22 and dehydrated.

<Effect of Embodiment>
As described above, according to the present embodiment, in the washing process and the rinsing process, the drum 22 and the stirring body 24 rotate so that the rotation speed of the stirring body 24 is faster than the rotation speed of the drum 22. Thereby, the laundry in the drum 22 is not only struck by the inner peripheral surface of the drum 22 by the stirring by the baffle 23, but is also rubbed by the blades 24a of the rotating stirring body 24. Therefore, compared with the structure in which the laundry is only stirred by the baffle 23, the cleaning performance and the rinsing performance can be improved.

  Furthermore, according to the present embodiment, as a configuration of the drive unit 30 for rotating the stirring body 24 faster than the drum 22, the stirring body 24 is rotated at a rotational speed equal to that of the rotor 110 and compared with the stirring body 24. Thus, the drum 22 that requires a large torque is rotated by decelerating the rotation of the rotor 110. As a result, the drum 22 and the stirrer 24 can be rotated at a rotational speed equal to that of the rotor 110 and the stirrer 24 can be rotated by increasing the rotation of the rotor 110. The torque generated by the drive motor 100 during driving can be reduced, and the power consumption of the drive motor 100 can be reduced.

  Furthermore, according to the present embodiment, the rotor 110 of the drive motor 100 and the stirring body 24 are connected by the single blade shaft 200. Therefore, unlike the configuration in which the rotating shaft of the rotor 110 and the rotating shaft of the stirring member 24 are provided and connected to each other, when the drive unit 30 is assembled, it is not necessary to align the centers of the two rotating shafts. It becomes. Therefore, the assembly of the drive unit 30 becomes easy. In addition, there is no need to worry about an axial deviation that occurs between the two rotating shafts.

  In addition, according to the present embodiment, the space generated between the first rolling bearing 513 and the second rolling bearing 523 in order to satisfactorily support the load by the drum 22 by the drum shaft 300 is disposed in the planetary gear mechanism 400. Since it is used as a space, the size of the drive unit 30 can be reduced in the axial direction of the drum shaft 300. 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, the drum shaft 300 is fixed to the internal gear 420, and the tip end portion 442b of the carrier shaft 442 provided on the planetary carrier 440 is projected out of the drum shaft 300, and the projected tip end portion 442b is projected. Since the clutch mechanism 600 is involved in this, the operation of the planetary gear mechanism 400 is switched, and the form of the drive unit 30 is changed to the first form in which the blade shaft 200 and the drum shaft 300 rotate separately, the blade shaft 200 and the drum. Switching is made between the second mode in which the shaft 300 rotates integrally. Therefore, even when the planetary gear mechanism 400 is configured to be included in the drum shaft 300 as a result of the configuration in which the planetary gear mechanism 400 is sandwiched between the first rolling bearing 513 and the second rolling bearing 523, Switching between the first form and the second form can be performed satisfactorily. In addition, by adjusting the number of teeth of the sun gear 410 and the internal gear 420, the reduction ratio between the rotor 110 and the drum shaft 300 can be set, and a wide range of reduction ratios can be set.

  Furthermore, according to the present embodiment, the planetary gear 430 is constituted by the first gear 431 and the second gear 432, so that the drive unit 30 fixes the drum shaft 300 to the internal gear 420. When the rotation of the drum shaft 300 is reduced, the drum shaft 300 and the blade shaft 200 can be rotated in the same direction. Therefore, since the stirring force by the stirring body 24 can be applied in the same direction as the rotation direction of the drum 22, the stirring force of the laundry in the drum 22 can be increased.

  Furthermore, according to the present embodiment, the clutch body 610 fitted to the tip end portion 442b of the carrier shaft 442 protruding outside the drum shaft 300 is moved in the axial direction of the drum shaft 300 by the moving mechanism portion DM. The spline 611 of the clutch body 610 and the spline 525 of the bearing unit 500 are engaged, or the engaging flange portion 613 of the clutch body 610 and the engaged recess 114 of the rotor 110 are engaged. Thus, the clutch mechanism 600 that switches the configuration of the drive unit 30 between the first configuration and the second configuration by being related to the carrier shaft 442, that is, the planet carrier 440, can be specifically realized. Moreover, the spline 525 that engages with the spline 611 of the clutch body 610 is formed in the rear unit 520 in which the second rolling bearing 523 that is concentric with the carrier shaft 442 into which the clutch body 610 is fitted is formed. The center and the center of the spline 525 can be matched with high accuracy. Therefore, the splines 611 and 525 can be engaged with each other with high accuracy.

  Furthermore, according to the present embodiment, the clutch flange 613 is engaged with the engaged recess 114 when the clutch body 610 is moved by the elastic force of the clutch spring 620, and the clutch body 610 is engaged by this engagement. When rotating together with the rotor 110, the pressing portion 633 is separated from the clutch body 610. For this reason, 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.

  Furthermore, according to the present embodiment, the bearing unit 500 includes a planetary unit including the front unit 510 including the first rolling bearing 513 and the rear unit 520 including the second rolling bearing 523 in the axial direction of the drum shaft 300. The drum shaft 300 that includes the gear mechanism 400 is configured to cover the front and rear sides. When the bearing unit 500 is not divided, as shown in FIG. 13, in order to secure an opening O into which the drum shaft 300 containing the planetary gear mechanism 400 is inserted in the bearing unit 500, for example, the drum shaft 300 The second rolling bearing 523 having a larger outer diameter than that of the housing portion 300c is used, and the thickness of the rear shaft portion 300b of the drum shaft 300 is increased as the outer diameter of the second rolling bearing 523 is increased. It is necessary to take. According to the configuration of the present embodiment, the drum shaft 300 that encloses the planetary gear mechanism 400 can be accommodated in the bearing unit 500 by coupling the front unit 510 and the rear unit 520, which is larger than necessary. It is avoided that the first rolling bearing 513 and the second rolling bearing 523 are used and the drum shaft 300 becomes unnecessarily heavy due to an increase in thickness.

  Further, according to the present embodiment, since the front unit 510 and the rear unit 520 are coupled by inlay fitting, the first rolling bearing is provided even when the bearing unit 500 is divided. The center P1 of 513 and the center P2 of the second rolling bearing 523 can be made to coincide with each other with high accuracy. For this reason, it can prevent that the drum axis | shaft 300 cannot rotate smoothly by the axial shift of the center P1 of the 1st rolling bearing 513, and the 2nd rolling bearing 523.

  Furthermore, according to the above embodiment, the stator 120 of the drive motor 100 is fixed to the rear unit 520 provided with the second rolling bearing 523, so that the center of the stator 120 is set to the center P2 of the second rolling bearing 523. It can be matched with high accuracy. Since the center of the second rolling bearing 523 coincides with the center of the rotor 110 fixed to the blade shaft 200, the center of the stator 120 coincides with the center of the rotor 110 with high accuracy. Thereby, the clearance S (see FIG. 2) between the rotor 110 and the stator 120 can be kept constant, and the drive motor 100 can be rotated stably.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments and the like, and various modifications can be made to the embodiments of the present invention in addition to the above. is there.

  For example, in the above embodiment, the engagement of the spline 611 of the clutch body 610 and the spline 525 of the bearing unit 500 restricts the rotation of the clutch body 610 relative to the bearing unit 500 in the circumferential direction. Further, the engagement of the engagement flange portion 613 of the clutch body 610 and the engaged recess 114 of the rotor 110 restricts the rotation of the clutch body 610 in the circumferential direction relative to the rotor 110. 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 embodiment. It may be a configuration. For example, even when a projection is formed at the front end portion and the rear end portion of the clutch body 610, a recess or hole is formed in the bearing unit 500 and the rotor 110, and the projection is fitted into the recess or hole. good.

  Further, in the above embodiment, the cover unit 521 that covers the housing part 300 c of the drum shaft 300 is provided in the rear unit 520. However, the cover unit 521 may be provided in the front unit 510, or the cover unit 521 may be provided so as to be divided into the front unit 510 and the rear unit 520.

  Further, in the above-described embodiment, the fitted recess 514 is provided in the front unit 510 and the fitting rib 527 is provided in the rear unit 520. However, the fitting rib 527 may be provided on the front unit 510, and the fitting recessed portion 514 may be provided on the rear unit 520. In the above-described embodiment, the fitting rib 527 and the fitting recessed portion 514 are in contact with the outer peripheral surfaces 527a and 514a during fitting. However, the fitting rib 527 and the fitted recess 514 may be configured such that their inner peripheral surfaces are in contact with each other, or both the outer peripheral surface and the inner peripheral surface may be in contact. In this case, when the inner peripheral surfaces are in contact with each other, each of the inner peripheral surfaces has a circular shape concentric with the rolling bearing corresponding to each inner peripheral surface. Furthermore, the circumferential surfaces that contact each other may not be completely circular, but may have a shape in which the circle is interrupted. That is, the circumferential surfaces that are in contact with each other may have a circular arc shape. That is, if inlay fitting is possible between a circumferential surface having a circular shape or an arc shape concentric with the first rolling bearing 514 and a circumferential surface having a circular shape or arc shape concentric with the second rolling bearing 523, each circumference The shape of the portion where the surface is formed may be any shape.

  Furthermore, in the above-described embodiment, the drum 22 rotates around the tilt axis tilted with respect to the horizontal direction. However, the drum type washing machine 1 may be configured such that the drum 22 rotates about the horizontal axis.

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

  In addition, the embodiment of the present invention can be variously modified as appropriate within the scope of the technical idea shown in the claims.

10 housing
20 Outer tank
22 drums
24 Stirring body (rotating body)
24a Feather (projection)
30 Drive unit (drive unit)
100 drive motor
110 rotor
114 Engaged recess (second engaged part)
120 stator
200 Blade axis (first rotation axis)
202 Regulatory ring
300 Drum shaft (second rotary shaft)
300a Front shaft (first shaft)
300b Rear shaft (second shaft)
300c housing part
400 Planetary gear mechanism (transmission mechanism, reduction mechanism)
410 Sun gear
420 Internal gear
430 Planetary gear
431 1st gear
432 Second gear
440 Planetary Carrier
442 Carrier shaft (shaft)
500 Bearing unit
510 Front unit (first unit)
513 First rolling bearing (first bearing)
514 Fitted recess 514a Outer peripheral surface (first peripheral surface)
520 Rear unit (second unit)
523 Second rolling bearing (second bearing)
525 Spline (first engaged part)
526 Mounting boss (fixed part)
527 Fitting rib (convex)
527a Outer peripheral surface (second peripheral surface)
600 Clutch mechanism
610 Clutch body
611 spline (first engaging part)
613 Engagement flange (second engagement part)
620 Clutch spring (elastic member)
630 Clutch lever
633 Pressing part (pressing member)
640 Lever support
650 Clutch drive device
660 Mounting plate
DM moving mechanism

Claims (5)

An outer tub disposed in the housing;
A drum arranged in the outer tub and rotatable around a horizontal axis or an inclined axis inclined with respect to the horizontal direction;
A baffle provided on the inner peripheral surface of the drum;
A rotating body disposed at the rear of the drum and having a protrusion on the surface that contacts the laundry;
A drive unit that rotates the drum and the rotating body such that the rotational speed of the rotating body is faster than the rotational speed of the drum;
The drive unit is
A drive motor;
A first rotating shaft coupled to the rotating body and transmitting torque of the drive motor to the rotating body;
A speed change mechanism that changes the rotation of the rotor of the drive motor;
A second rotation shaft coupled to the drum and transmitting torque of the drive motor to the drum, and including the first rotation shaft and the speed change mechanism;
A bearing unit having a first bearing and a second bearing arranged so as to sandwich the speed change mechanism, and rotatably supporting the second rotating shaft 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 outside the first shaft portion and the second shaft portion. A bulge, and a housing portion for housing the speed change mechanism,
The bearing unit includes a first unit including the first bearing and a second unit including the second bearing, and the first unit and the second unit are in the axial direction of the second rotating shaft, and Combined from both sides of the housing part ,
The speed change mechanism includes a speed reduction mechanism for reducing the rotation of the rotor,
The reduction mechanism includes a sun gear that rotates as the rotor of the drive motor rotates, an annular internal gear that surrounds the sun gear, and a plurality of planetary gears that are interposed between the sun gear and the internal gear. And a planet carrier that rotatably holds these planetary gears,
The second rotation shaft is fixed to the internal gear and rotates with the rotation of the internal gear,
The planetary carrier includes a shaft portion that is coaxial with the second rotation shaft and has a tip portion protruding from the second rotation shaft to the rotor side,
The drive unit further includes a clutch mechanism unit,
The clutch mechanism portion is provided so as to be related to a tip portion of the shaft portion protruding from the second rotation shaft, and the shaft portion cannot be rotated so that the first rotation shaft and the second rotation shaft are moved. A first mode in which the rotation speed of the second rotation shaft is made slower than the rotation speed of the first rotation shaft in accordance with a reduction ratio by the speed change mechanism, and the shaft portion rotates with the rotor. Thus, the form of the drive unit is switched between a second form in which the first rotating shaft, the speed reduction mechanism, and the second rotating shaft are integrally rotated at a rotational speed equal to the rotational speed of the rotor.
A drum-type washing machine characterized by that. In the drum type washing machine according to claim 1,
The first unit has a first circumferential surface having a circular or arc shape concentric with the first bearing, and the second unit has a first circular surface or arc shape concentric with the second bearing. 2 peripheral surfaces,
The first unit and the second unit are coupled by a spigot fitting between the first peripheral surface and the second peripheral surface.
A drum-type washing machine characterized by that. In the drum type washing machine according to claim 1 or 2,
The bearing unit is provided with a fixing portion for fixing the stator of the motor to the second unit, while the second unit is positioned on the drive motor side.
A drum-type washing machine characterized by that. In the drum type washing machine according to any one of claims 1 to 3 ,
The clutch mechanism portion is fitted into the tip portion, and a clutch body that is allowed to move in the axial direction of the shaft portion with respect to the tip portion and is restricted from rotating in the circumferential direction of the shaft portion; A moving mechanism for moving the clutch body in the axial direction,
A first engagement portion and a second engagement portion are provided at the end on the bearing unit side and the end on the rotor side of the clutch body, respectively.
The second unit located on the drive motor side is provided with a first engaged portion,
The rotor is provided with a second engaged portion,
When the clutch body is moved to the second unit side by the moving mechanism and the first engaging portion is engaged with the first engaged portion, the clutch body rotates in the circumferential direction with respect to the second unit. The movement is restricted, and the shaft portion cannot rotate,
When the clutch body is moved to the rotor side by the moving mechanism and the second engagement portion is engaged with the second engaged portion, the rotation of the clutch body in the circumferential direction with respect to the rotor is restricted. The shaft portion can be rotated together with the rotor,
A drum-type washing machine characterized by that. In the drum type washing machine according to claim 4 ,
The moving mechanism section is
An elastic member that is interposed between the clutch body and the bearing unit, moves the clutch body toward the rotor side by an elastic force, and engages the second engagement portion with the second engaged portion; ,
When the clutch body is pushed, the clutch body is moved to the bearing unit side, and when the first engagement portion is engaged with the first engaged portion, the clutch body is in contact with the second engagement portion. A pressing member that is separated from the clutch body in a state in which the joint portion engages with the second engaged portion,
A drum-type washing machine characterized by that.

Images