Drum rotation device and laundry treating apparatus comprising same

Abstract

The present invention relates to a drum rotation device and a laundry treating apparatus comprising same. A clutch (410) and a rotor (230) of the present invention may be respectively equipped with a clutch gear (417) and a coupling gear (352) that engage with each other in the axial direction. The clutch gear (417) may comprise: clutch inclined portions (417A), each having a height in the axial direction that gradually decreases along the circumferential direction of the clutch (410); and a first clutch catch portion (417B1) and second clutch catch portion (417B2) provided respectively at both ends of each clutch inclined portion (417A) and extending in the axial direction. The clutch inclined portions (417A) can align the clutch (410) and the rotor (230) in the circumferential direction, and the first and second clutch catch portions (417B) can support the clutch (410) and the rotor (230) in the reverse rotation direction during rapid deceleration of the rotor (230).

Description

Drum rotating device and clothing processing device including the same

[0001] The present invention relates to a drum rotating device and a clothing processing device including the same.

[0002] Generally, a garment processing device refers to a device that washes laundry or dries washed laundry. The garment processing device includes a washing machine and a dryer. Among these, the washing machine can wash laundry through washing, rinsing, and spinning processes to remove contaminants from laundry, such as clothing and bedding.

[0003] Recently, various types of washing machines have been commercialized. For example, there are vertical washing machines in which the drum receiving the laundry rotates along a vertical axis, and drum-type washing machines that rotate around a horizontal or inclined axis. All of these washing machines are driven by motors.

[0004] A drum-type washing machine can perform a series of washing processes, such as washing, rinsing, and spinning, by rotating a drum containing laundry. In this process, high torque rotational power at low speeds is required during washing or rinsing, where laundry containing a large amount of water is rotated. On the other hand, low torque rotational power at high speeds is required during the spinning process, where laundry is rotated until it contains almost no water.

[0005] As such, the drum drive unit that drives the washing machine needs to provide various rotational forces and rotational speeds depending on the driving mode. To this end, a reduction gear and a clutch are used in the drum drive unit. For example, Korean Published Patent No. 10-2020-0089604 (Priority Patent 1), Korean Published Patent No. 10-2023-0090484 (Prior Patent 2), and Korean Registered Patent No. 10-1920812 (Prior Patent 3) disclose a technology for reducing the motor by installing multiple gears, such as a planetary gear assembly, between the motor and the output shaft. The clutch can change the torque and rotational speed of the output shaft coupled to the rotational shaft of the drum by controlling the driving of some of the multiple gears.

[0006] However, the aforementioned prior patents make it difficult to shift gears while the drum is in operation. This is because it is difficult for the clutch and the motor (rotor) to engage while the drum drive unit is rotating. Of course, the clutch and the motor can engage if the clutch is pushed toward the motor with strong force, but this process causes problems such as significant vibration and noise.

[0007] In particular, when the clutch and motor are coupled, if the gear structures equipped in the clutch and motor mesh without being aligned, not only is vibration and noise generated, but there is also a problem of parts wearing out due to strong impact.

[0008] Furthermore, if the motor rapidly decelerates during the operation of the garment processing device, there is a risk that the clutch gear may slide axially along the motor-side gear due to the rotational process. This is because if the gear structures equipped in the clutch and motor, respectively, include inclined or curved surfaces, they may slide over each other. During this process, the clutch and motor components may repeatedly collide with each other, potentially generating significant noise and vibration.

[0009] Meanwhile, the aforementioned prior patents perform a transmission function as the clutch moves between a first position and a second position. In other words, the clutches in the prior patents have only two positions and cannot be constrained to the neutral position between them. As such, the prior patents cannot finely control the displacement of the clutch. Therefore, there is a limitation in that various functions, such as speed synchronization, cannot be implemented through the precise constraint of the clutch's displacement.

[0010] The present invention is intended to solve the problems of the prior art as described above, and the objective of the present invention is to enable gear shifting by engaging the clutch with the mating part (rotor) even during the operation (rotation) of the drum rotation device.

[0011] Another objective of the present invention is to ensure that, during the process in which the clutch gear (clutch gear) and the rotor gear (coupling gear) mesh with each other, the two gears slide against each other and the direction of engagement is aligned.

[0012] Another objective of the present invention is to prevent the two gears from moving axially apart from each other along the inclined portions of each other when the rotor is decelerated.

[0013] Another objective of the present invention is to allow the clutch to move between a first position (locked state) and a second position (rotated state), while ensuring that the displacement of the clutch is constrained at a third position (neutral state) between the first and second positions.

[0014] According to the features of the present invention for achieving the above-mentioned purpose, the clutch and rotor constituting the present invention may each be provided with a clutch gear and a coupling gear that are coupled to each other in the axial direction. In this case, the clutch gear may include a clutch inclined portion in which the axial height gradually decreases along the circumferential direction of the clutch, a first clutch engaging portion extending in the axial direction from one end of the clutch inclined portion, and a second clutch engaging portion provided between one end and the other end of the clutch inclined portion. The clutch inclined portion can align the clutch and the rotor in the circumferential direction, and the two clutch engaging portions can support the clutch and the rotor in the reverse rotational direction during rapid deceleration of the rotor.

[0015] The present invention may include a motor comprising a stator and a rotor that rotates relative to the stator and rotates the motor shaft, and a clutch that moves in the axial direction of the motor shaft and is connected to the rotor. The clutch may be moved in the axial direction by a clutch driving device.

[0016] The above-mentioned clutch inclined portion can have its axial height continuously lowered along the circumferential direction of the clutch.

[0017] The first clutch engaging portion may form a step by connecting the upper portion, which has the highest axial height of the clutch inclined portion, and the lower portion, which has the lowest axial height of an adjacent clutch inclined portion.

[0018] The second clutch engaging portion may form a step by connecting a first end portion, which has an axial height lower than the upper end portion of the clutch inclined portion, and a second end portion, which has an axial height lower than the first end portion and an axial height higher than the lower end portion.

[0019] At both ends of one clutch gear tooth constituting the above clutch gear, a top portion having the highest axial height and a bottom portion having the lowest axial height may be provided, respectively.

[0020] The above clutch inclined portion may have an axial height that gradually decreases from the top portion toward the bottom portion.

[0021] The second clutch engaging part may be provided between the top part and the bottom part.

[0022] The first clutch engaging portion may have an axial height higher than the second clutch engaging portion.

[0023] At both ends of a single gear tooth constituting the above clutch gear, a top portion and a bottom portion may be provided, respectively.

[0024] The above clutch inclined portion may include a first clutch inclined portion in which the axial height gradually decreases from the top portion toward the upper end of the second clutch engaging portion, and a second clutch inclined portion in which the axial height gradually decreases from the second clutch engaging portion toward the bottom portion.

[0025] The upper end of the first clutch engaging part may be formed on the top part.

[0026] The lower end of the second clutch inclined portion can be formed in the bottom portion.

[0027] Based on a reference line extending in the circumferential direction of the above clutch, the second clutch inclination portion may have an inclination angle that is smaller than or equal to the first clutch inclination portion.

[0028] Based on the second clutch engaging portion, two different clutch inclined portions may be provided on both sides of the clutch engaging portion.

[0029] The two clutch inclined portions mentioned above may have different axial heights relative to the clutch engaging portion.

[0030] The first clutch engaging part and the second clutch engaging part may be provided in a direction perpendicular to the circumferential direction of the clutch.

[0031] The axial height of the second clutch engaging portion may be lower than the axial height of the clutch inclined portion.

[0032] The circumferential length between the top part and the second clutch engaging part may be longer than or equal to the circumferential length between the second clutch engaging part and the bottom part.

[0033] The gear teeth of the above clutch gear may include the clutch inclined portion, the first clutch engaging portion, and the second clutch engaging portion.

[0034] The first clutch engagement portion above connects the top portion, which has the highest axial height, and the bottom portion, which has the lowest axial height of an adjacent clutch gear tooth, and can be extended in the axial direction.

[0035] At least one of the boundary between the above-mentioned clutch inclined portion and the above-mentioned second clutch engaging portion and the upper end of the above-mentioned first clutch engaging portion may be formed as a curved surface.

[0036] The height of the above-mentioned clutch slope portion protruding toward the rotor along the circumferential direction of the clutch can gradually decrease.

[0037] The gear teeth of the coupling gear may include a coupling inclined portion guided by the clutch inclined portion, a first coupling engaging portion that is in close contact with the first clutch engaging portion in the circumferential direction of the clutch, and a second coupling engaging portion that is in close contact with the second clutch engaging portion in the circumferential direction of the clutch.

[0038] A top portion and a bottom portion may be provided at each end of a single gear tooth constituting the coupling gear. The coupling gear may include a coupling inclined portion that is guided by the clutch inclined portion, wherein the axial height gradually decreases from the top portion toward the bottom portion. The coupling gear may include a second coupling engaging portion that is provided between the top portion and the bottom portion and extends in the axial direction. The second coupling engaging portion may be in close contact with the second clutch engaging portion in the circumferential direction of the clutch.

[0039] The clutch can be switched from the locked state through the neutral state to the rotational state. A synchronization mode can be implemented in which the rotational speed of the clutch is synchronized with the rotational speed of the rotor in the neutral state. The synchronization mode may include a first synchronization mode in which the rotor rotates without shifting and the clutch is moved by the clutch drive device to switch from the locked state to the neutral state. The synchronization mode may include a second synchronization mode in which the rotor is decelerated and the clutch is accelerated by the deceleration of the rotor.

[0040] When the speeds of the clutch and the rotor are synchronized through the second synchronization mode, the clutch can move in the direction of the rotor and be coupled to the coupling unit of the rotor.

[0041] The above clutch driving device may be equipped with driving gears that move the clutch linearly in the axial direction.

[0042] The above drive gears may include a pinion portion rotated by a drive motor of the clutch drive device and a rack portion linked to the pinion portion and moving linearly in the axial direction.

[0043] The above clutch is coupled to the above rack portion and can move linearly in the above axial direction.

[0044] Corresponding inclined portions may be formed on the clutch gear and the coupling gear, respectively.

[0045] The clutch gear and the coupling gear may form a plurality of spaced-apart locking portions along the circumferential direction of the clutch within a single meshed gear tooth. The plurality of locking portions may have different axial heights.

[0046] The drum rotating device according to the present invention and the clothing processing device including the same, as described above, have the following effects.

[0047] In the present invention, a clutch for shifting gears of a drum rotating device and a rotor coupled to the clutch may each be equipped with a clutch gear and a coupling gear. At this time, the clutch gear and the coupling gear may each be provided with an inclined portion whose height gradually decreases along the rotational direction of the rotor. This inclined portion can induce the clutch gear and the coupling gear to slide and mesh accurately even if they are coupled without being precisely aligned. Therefore, the clutch can engage with the rotor and shift gears even while the rotor is rotating. Since the clutch can engage with the rotor while the rotor is rotating, stopping the rotor is unnecessary, and shifting gears via the clutch can be achieved more quickly.

[0048] In addition, in the present invention, the clutch gear and the coupling gear may each be provided with a locking portion that is supported in the opposite rotational direction (circumferential direction). These two locking portions can be supported by being in close contact in the opposite rotational direction when the rotor is rapidly decelerated. Therefore, even if the rotor is rapidly decelerated, it is possible to prevent the inclined portion of the clutch gear from moving axially along the inclined portion of the coupling gear, and the driving stability of the drum rotation device can be improved.

[0049] In particular, the present invention can prevent collisions between the clutch and the rotor that occur during the process in which the inclined portion of the clutch gear moves axially along the inclined portion of the coupling gear and then returns to its original position when the rotor is rapidly decelerating. Therefore, not only is wear on the parts prevented, but noise caused by collisions between the parts is also effectively prevented.

[0050] In addition, the clutch gear in the present invention may include a first clutch engaging portion supported by the rotor in a first rotational direction and a second clutch engaging portion supported by the rotor in a second rotational direction, which is the reverse rotational direction. Accordingly, the clutch and the rotor are supported in opposite directions, thereby enabling stable operation of the drum rotation device.

[0051] In addition, in the present invention, different first clutch inclined portions and second clutch inclined portions may be provided at each end of the second clutch engaging portion. The first clutch inclined portion can induce alignment between the clutch and the rotor, and the second clutch inclined portion can reduce shock during the engagement process between the clutch and the rotor. Therefore, the clutch and the rotor can be engaged more smoothly, and the operational reliability of the clutch can also be improved.

[0052] Furthermore, in the present invention, the clutch can move linearly by means of a drive module. The drive gears of the drive module convert the rotational motion of the drive motor into linear motion to move the clutch. Since the gears interlock to move and support the clutch in this manner, the displacement of the clutch can be firmly constrained without the need for elastic members such as springs. Because the clutch with constrained displacement has very high resistance to external forces separating the clutch from the rotor, vibrations generated during the process of the clutch separating from and re-engaging the rotor, as well as the resulting wear of parts, can be prevented.

[0053] In addition, in the present invention, the clutch can switch between a locked state (high gear ratio mode) and a rotating state (low gear ratio mode) while moving linearly along the surface of the ring gear. At this time, the clutch can have a neutral state between the locked state and the rotating state. The clutch in the neutral state can be synchronized with the rotation of the rotor as its rotational speed gradually increases. The clutch, which is synchronized with the rotor in speed, can naturally engage with the rotor without significant shock or noise, and mode switching is possible without stopping the motor. Therefore, the mode switching speed of the drum rotation device can be improved, and the stability during mode switching is also enhanced.

[0054] Furthermore, in the present invention, the clutch moves linearly in conjunction with the drive gears of the drive module, so it can have various displacements. The clutch is constrained not only to the first and second positions but also to various displacements in between, thereby enabling a synchronization mode. As such, the present invention has the advantage of being able to implement various functions through the precise control of the clutch.

[0055] In particular, in the present invention, the clutch can be connected to the rotor in a state where the speeds of the clutch and the rotor are synchronized. At this time, the synchronization mode may include a first synchronization mode in which the clutch is released from a locked state, and a second synchronization mode in which the clutch accelerates as the rotor decelerates. Through these stepwise synchronization modes, the clutch can rotate at the same speed as the rotor, and accordingly, there is an effect of reducing vibration and noise generated at the moment the clutch engages with the rotor.

[0056] Furthermore, in the present invention, the clutch engages with the rotor after passing through a neutral state, and the inclined surface structure of the clutch gear is organically combined to reduce noise and vibration during clutch engagement. Therefore, the present invention can also achieve improved driving stability and prevent parts wear.

[0057] FIG. 1 is a perspective view showing the structure of an embodiment of a clothing processing device to which a drum rotation device according to the present invention is applied.

[0058] FIG. 2 is a perspective view showing the structure of a casing and a tub constituting an embodiment of a clothing processing device according to the present invention.

[0059] FIG. 3 is a perspective view showing an embodiment of a drum rotation device according to the present invention.

[0060] FIG. 4 is a cross-sectional view along the line IV-IV' of FIG. 3.

[0061] FIG. 5 is a cross-sectional view showing an embodiment of a drum rotation device according to the present invention and a state in which a drum shaft is coupled.

[0062] FIG. 6 is a cross-sectional view along the line VI-VI' of FIG. 3.

[0063] FIG. 7 is an exploded perspective view showing the parts constituting an embodiment of a drum rotation device according to the present invention.

[0064] FIG. 8 is a perspective view showing the parts constituting an embodiment of a drum rotation device according to the present invention disassembled and shown at a different angle from FIG. 7.

[0065] FIG. 9 is a perspective view showing a state in which a clutch and a coupling unit constituting an embodiment of the present invention are engaged with each other.

[0066] FIG. 10 is a perspective view showing a clutch and a coupling unit separated from each other, constituting an embodiment of the present invention.

[0067] FIG. 11 is a cross-sectional view showing the state in which a clutch and a coupling unit constituting an embodiment of the present invention are engaged with each other.

[0068] FIG. 12 is a cross-sectional view showing the state in which a clutch gear and a coupling gear constituting an embodiment of the present invention are engaged with each other.

[0069] FIG. 13 is a front view showing the state in which the clutch gear and the coupling gear constituting an embodiment of the present invention are separated from each other.

[0070] FIG. 14 is a front view showing the state in which a clutch gear and a coupling gear constituting an embodiment of the present invention are engaged with each other.

[0071] FIG. 15 is a front view showing the state in which a clutch gear and a coupling gear constituting an embodiment of the present invention are engaged with each other.

[0072] FIGS. 16 to 19 are operation state diagrams showing the process of a clutch gear and a coupling gear engaging with each other, constituting an embodiment of the present invention.

[0073] FIG. 20 is an enlarged view showing a second embodiment of a clutch gear constituting an embodiment of the present invention.

[0074] FIG. 21 is an enlarged view showing a third embodiment of a clutch gear constituting an embodiment of the present invention.

[0075] Hereinafter, some embodiments of the present invention will be described in detail with reference to exemplary drawings. It should be noted that in assigning reference numerals to the components of each drawing, the same components are given the same reference numeral whenever possible, even if they are shown in different drawings. Furthermore, in describing the embodiments of the present invention, if it is determined that a detailed description of related known components or functions would hinder understanding of the embodiments of the present invention, such detailed description is omitted.

[0076] The present invention relates to a drum rotation device (100) and a clothing processing device including the same. Here, the clothing processing device refers to a home appliance in which an internal drum (30) rotates, such as a washing machine or a dryer. The clothing processing device may also include a home appliance capable of both washing and drying. Below, the clothing processing device will be described using a washing machine as an example.

[0077] FIG. 1 illustrates a washing machine, which is a clothing processing device to which a drum rotation device (100) according to the present embodiment is applied. As shown in FIG. 1, the frame of the washing machine may be formed by a casing (10) in the shape of a roughly cuboid. The casing (10) may include a frame (11) that constitutes the exterior. A door (15) may be placed at the front of the casing (10). When the door (15) is opened, a storage space (S1) inside the washing machine may be exposed. A user may put laundry into the storage space (S1).

[0078] For reference, in the following, "front" refers to the front of the casing (10) in which the door is placed, and "rear" refers to the rear of the casing (10) opposite to this. Based on FIG. 1, the user can put laundry in from the rear and take it out from the front. In the drawing, the reference numeral F indicates the front, and the reference numeral R indicates the rear.

[0079] The storage space (S1) may be formed inside the drum (30). The drum (30) may be a rotating body and may have a shape that surrounds the storage space (S1). The drum (30) may be coupled to a spider (60, see FIG. 2) to be described below. When the spider (60) is rotated by the drum rotation device (100), the drum (30) may also be rotated together.

[0080] FIG. 2 illustrates the structure of the frame (11) and tub (50) forming the skeleton of the casing (10). For reference, the drum rotation device (100) is positioned between the rear of the tub (50) and the casing (10) and is not visible in FIG. 2. The tub (50) can surround the drum (30). That is, the tub (50) becomes a kind of outer tank, and the drum (30) becomes an inner tank. Reference numeral S2 is a rotational space surrounded by the tub (50), and the drum (30) can be placed in the rotational space (S2). The tub (50) is coupled to the casing (10) and does not rotate, while the drum (30) can rotate relative to the tub (50).

[0081] FIG. 3 illustrates the rear structure of the tub (50). For reference, in FIG. 3, the casing (10) covering the rear of the tub (50) is removed, so the rear of the tub (50) is exposed. A motor (200) of the drum rotation device (100) may be placed at the rear center of the tub (50). The motor (200) can generate rotational force by receiving external power. FIG. 3 illustrates a rotor (230) constituting the motor (200), and a stator (220) and a gear assembly (300), which will be described later, are placed inside the rotor (230).

[0082] The above tub (50) may include a tub body (51) having a roughly cylindrical shape. The front of the tub body (51) is open and becomes the entrance to the rotation space (S2). The motor (200) may be positioned at the rear of the tub body (51). A reinforcing material (53, see FIG. 4) made of metal may be embedded in the tub body (51) to reinforce strength. The reinforcing material (53) may be embedded in the tub body (51) by an insert injection molding method.

[0083] A rear fence (55) may be provided on the rear of the tub body (51). The rear fence (55) protrudes backward from the rear of the tub (50). The rear fence (55) may be approximately ring-shaped. The rear fence (55) may be arranged around the motor (200) and the gear assembly (300). A plurality of reinforcing ribs may be arranged around the rear fence (55).

[0084] In this embodiment, the rear fence (55) and the motor (200) are spaced apart from each other, so that a certain space is provided between them. A drive module (401) constituting a clutch drive device (400), which will be described below, can be placed in the space. As described below, the gear assembly (300) can be miniaturized, and accordingly, the diameter of the motor (200) can also be reduced. When the motor (200) is miniaturized, the gap between the motor (200) and the rear fence (55) widens, so that a large space can be secured for placing the drive module (401).

[0085] Referring to FIG. 4, the internal structure of the drum rotation device (100) is illustrated. The drum rotation device (100) may be positioned at the rear of the tub body (51), and the spider (60) may be positioned at the front of the drum rotation device (100). The drum rotation device (100) and the spider (60) may be connected by the drum shaft (80). The drum shaft (80) may form an output shaft together with the output section (363) of the carrier body (361) to be described below. Hereinafter, the output shaft refers to the combination of the drum shaft (80) and the output section (363). Hereinafter, the input shaft refers to the sun gear (370).

[0086] The carrier body (361) constituting the carrier (360) is a component constituting the gear assembly (300) and rotates together with the drum shaft (80). The carrier body (361) is coupled with the drum shaft (80) and rotates together with it. Therefore, the drum shaft (80) can be seen as being rotated by the carrier body (361).

[0087] Looking at the drum shaft (80), the drum shaft (80) includes a cylindrical shaft body (85). The gear assembly (300) is coupled to one end of the shaft body (85). More precisely, a shaft coupling groove (83) is formed at one end of the shaft body (85), and the output part (363) of the carrier (360), which will be described later, is inserted and fixed into the shaft coupling groove (83). The spider (60) is coupled to the other end of the shaft body (85). Therefore, when the rotational force of the rotor (230) is transmitted to the drum shaft (80) through the carrier (360), the spider (60) and the drum (30) rotate together with the drum shaft (80).

[0088] At this time, the interior of the drum rotation device (100) can be divided into a first area and a second area. The first area and the second area can be divided based on a virtual partition line (L1) passing through the position where the sun gear (340) and the drum shaft (80) face each other. In FIG. 4, L1 represents a partition line (L1) passing through the part where the surface of the sun gear (340) and one end of the drum shaft (80) face each other. The partition line (L1) is in a direction perpendicular to the axial direction of the drum shaft (80) and extends in the radial direction of the sun gear (340). Here, the first area is formed in front of the partition line (L1), and the second area is formed behind the partition line (L1).

[0089] For reference, unless otherwise specified below, "axial direction" means the axial direction of the drum shaft (80), and "interlocking" means that the gears are joined in a state where they can interlock with each other.

[0090] In this embodiment, the carrier (360) and the drum shaft (80) can be coupled to each other in a first area. More precisely, the output portion (363) of the carrier body (361) and one end of the drum shaft (80) are coupled to each other in the first area. In the second area, the sun gear (340), ring gear (321, 330), and pinion gears (370) can mesh and rotate with each other. Thus, when the area where the output shaft is coupled and the area where the gears mesh and rotate are separated, the sun gear (340) can participate only in the interlocking of the gears regardless of the coupling of the output shaft. The sun gear (340) does not need to have a hollow shape or a shape protruding in the direction of the drum shaft (80) for coupling with the output shaft. Accordingly, the diameter of the sun gear (340) can be reduced, and the gear ratio between the sun gear (340) and the ring gear (321, 330) can be increased.

[0091] Meanwhile, in the present embodiment, the sun gear (340), the ring gear (321, 330), the pinion gears (370), and the clutch (410) may overlap each other in the radial direction of the gear assembly (300) in the second region. Therefore, the second region may also be referred to as an overlapping region. In this way, when the sun gear (340), the ring gear (321, 330), the pinion gears (370), and the clutch (410) overlap in the radial direction in the second region, the axial length of the drum rotation device (100) can be formed short, and since the axial distance between parts is shortened, stable axial alignment can be achieved.

[0092] FIG. 5 illustrates the drum rotation device (100) and the drum shaft (80) with the spider (60) and the tub (50) omitted. In this embodiment, the drum rotation device (100) includes a plurality of bearings. The plurality of bearings are positioned between parts that rotate relative to each other and serve to assist in the rotation of the parts. As previously described, in this embodiment, the sun gear (340) is separated from the output shaft and is installed and rotated independently. Accordingly, the overall length of the sun gear (340) can be formed to be short.

[0093] Meanwhile, since the rotor (230) of the motor (200) is coupled with the sun gear (340), the sun gear (340) aligns the axis of the rotor (230). This means that if the length of the sun gear (340) is shortened, the axial length for installing bearings is also shortened. In this embodiment, a plurality of bearings are arranged in the radial direction of the sun gear (340) to support the rotating parts at multiple points. Specifically, a first support bearing (B1) is arranged between the outer surface of the sun gear (340) and the inner surface of the rotational support part (321C), which is part of the ring gear (321, 330) described below. A second support bearing (B2) is arranged between the outer surface of the rotational support part (321C), which is part of the ring gear (321, 330), and the coupling unit (350).

[0094] At this time, the first support bearing (B1) and the second support bearing (B2) are arranged to overlap each other along the radial direction of the sun gear (340). In FIG. 5, L2 is a virtual line extending radially along the sun gear (340) and can pass through the first support bearing (B1) and the second support bearing (B2), respectively. When the first support bearing (B1) and the second support bearing (B2) are arranged radially relative to each other, the axial length can be prevented from increasing even if multiple bearings are arranged. In this embodiment, the sun gear (340) is independent of the output shaft, so the axial length can be shortened, and stable shaft alignment is possible because it is supported at multiple points in the axial direction by the first support bearing (B1) and the multiple pinion gears (370) to be described later.

[0095] Referring to FIG. 6, the motor (200), the gear assembly (300) positioned inside the motor (200), and the clutch drive device (400) for driving the clutch (410) are illustrated. As shown here, the gear assembly (300), the clutch (410), and the motor (200) can be arranged to overlap each other in the radial direction of the gear assembly (300). More precisely, the sun gear (340), the ring gear (321, 330), the pinion gears (370) constituting the gear assembly (300), the clutch (410), the stator (220), and the rotor (230) can be arranged to overlap each other in the radial direction of the gear assembly (300). Accordingly, the axial length of the drum rotation device (100) can be formed to be short.

[0096] The clutch drive device (400) that operates the clutch (410) may include a drive module (401). The drive module (401) may be positioned further forward than the motor (200). The drive module (401) of the clutch drive device (400) may be positioned further forward from the motor (200), i.e., toward the tub (50). The drive module (401) may be positioned radially outward from the motor (200). By positioning the drive module (401) so as to be spaced apart from the motor (200) in the axial and radial directions, respectively, the degree of freedom of installation may be increased. Furthermore, since the drive module (401) of the clutch drive device (400) is positioned outside the motor (200) rather than inside the narrow motor (200), accessibility is good, and connections such as wire harnesses can be easily made.

[0097] Referring to FIGS. 5 and FIGS. 6, the motor (200) is examined. The motor (200) includes a fixed stator (220) and a rotor (230) that rotates relative to the stator (220). The stator (220) may include a core (223) in which metal plates are laminated and an insulator (221) that surrounds the core (223). The insulator (221) prevents current flowing through a coil (not shown) wound on the teeth of the core (223) from being directly transmitted to the core (223). A permanent magnet (233) may be positioned in the rotor (230) so as to face the core (223). As another example, the core (223) and the coil may be provided in the rotor (230), and the permanent magnet (233) may be provided in the stator (220).

[0098] The rotor (230) may surround the stator (220). A driving space (S3) is formed inside the stator (220). The gear assembly (300) may be placed in the driving space (S3). More precisely, the sun gear (340), pinion gears (370), and ring gears (321, 330) constituting the gear assembly (300) may be placed in the driving space (S3). A clutch (410) may also be placed in the driving space (S3). All or part of the output portion (363) of the carrier (360) constituting the output shaft may protrude forward, i.e., toward the tub (50), from the driving space (S3) surrounded by the rotor (230).

[0099] Referring to FIGS. 7 and FIGS. 8, we will examine the components constituting the drum rotation device (100). For reference, the stator (220) is omitted in FIGS. 7 and FIGS. 8. First, looking at the rotor (230), a rotor body (231) surrounding the stator (220) can form the framework of the rotor (230). The rotor body (231) has a structure including a roughly circular top plate and a side plate extending forward (downward direction based on FIG. 7) from the top plate. The entire rotor body (231) can be rotated.

[0100] A rotor center hole (232) may be opened at the center of the rotor body (231). A coupling unit (350), which will be described later, may be disposed in the rotor center hole (232). A sun gear (340) coupled to the coupling unit (350) may rotate together with the rotor (230). Reference numeral 235 indicates a coupling hole into which a fixing projection (354) of a clutch coupling part (351) constituting the coupling unit (350) is inserted.

[0101] The motor (200) may be supported by a supporter (310). The supporter (310) may be fixed to the tub (50), and the motor (200) may be placed on the supporter (310). The supporter (310) may be fixed to the rear surface of the tub (50). The supporter (310) may have a supporter body (311) that is approximately ring-shaped. The drum shaft (80) may be placed inside the supporter body (311) so as to be spaced apart from the supporter body (311). The supporter (310) may also be a stator housing that fixes the stator (220).

[0102] The supporter (310) may be provided with a locking portion (315). The locking portion (315) locks the clutch (410). More precisely, when the clutch (410) moves forward, the locking projection (415) of the clutch (410) engages with the locking portion (315) of the supporter (310) and becomes non-rotating. To achieve this, the locking portion (315) may have a continuous toothed shape corresponding to the locking projection (415). As another example, the locking portion (315) may not be continuous and may be made into a projection structure that is intermittently arranged in the circumferential direction of the supporter body (311).

[0103] The supporter (310) may be provided with a motor support member (317) that supports the stator (220). The motor support member (317) may have a structure that protrudes rearward in the direction of the motor (200). The motor support member (317) may be inserted into a mounting hole (not shown) of the stator (220) so that the stator (220) can be fixed to the supporter (310).

[0104] A drive module (410) of a clutch drive device (400), which will be described later, may be disposed on the supporter (310). The drive module (410) may drive the clutch lever (420) while fixed to the supporter (310). The supporter (310) may be provided with a mounting arm (312), and the drive module (410) may be installed on the mounting arm (312). The mounting arm (312) may protrude in a direction perpendicular to the axial direction. As another example, the drive module (410) may be fixed directly to the tub (50) instead of the mounting arm (312). Reference numeral 408 is a sensor frame for fixing the movable sensor (not shown), and the sensor frame (408) may be fixed to the supporter (310).

[0105] Looking at the gear assembly (300) connected to the rotor (230), the gear assembly (300) may include a ring housing part (320), an internal gear part (330), a sun gear (340), a coupling unit (350), a carrier (360), and pinion gears (370). These may rotate in conjunction with each other. The interlocking structure of the gear assembly (300) will be examined in detail below.

[0106] The ring housing portion (320) and the internal gear portion (330) can form a ring gear (321, 330). That is, the ring gear (321, 330) may include the ring housing portion (320) and the internal gear portion (330). The internal gear portion (330) is positioned inside the ring housing portion (320). The ring housing portion (320) and the internal gear portion (330) can be coupled to each other and rotate or stop together. As another example, the ring housing portion (320) and the internal gear portion (330) can be made as a single unit.

[0107] The ring housing portion (320) may include a first housing (321) and a second housing (325). The first housing (321) and the second housing (325) may be joined together to form an empty space inside. More precisely, when the first housing (321) and the second housing (325) are joined together, an internal space (322) is formed inside. The sun gear (340) and the pinion gears (370) may interact with each other in the internal space (322). As another example, the ring housing portion (320) may be composed only of the first housing (321) or the second housing (325).

[0108] When the first housing (321) and the second housing (325) are combined, the ring housing portion (320) can be approximately cylindrical in shape. The center of the ring housing portion (320) can be penetrated along the axial direction. In this embodiment, the sun gear (340) passes through the center of the first housing (321), and the output portion (363) of the carrier (360) passes through the center of the second housing (325).

[0109] Referring to FIG. 7, the structure of the first housing (321) may include a guide plate (321A), a base plate (321B), and a rotational support part (321C). The guide plate (321A) is a ring structure that forms the side of the first housing (321). A guide tooth (323) may be provided on the surface of the guide plate (321A). The clutch (410) engages with the guide tooth (323). A sliding tooth (413) that engages with the guide tooth (323) is provided on the inner surface of the clutch (410). Even though the ring housing part (320) and the sliding tooth (413) engage with each other, they are not fixed to each other in the axial direction, so the clutch (410) can move linearly in the axial direction along the guide plate (321A).

[0110] Since the guide tooth (323) and the sliding tooth (413) mesh with each other, the rotation or stopping of the ring gear (321, 330), including the ring housing part (320), is linked to the clutch (410). When the rotation of the clutch (410) is locked, the rotation of the ring gear (321, 330) is also locked and does not rotate. When the clutch (410) is rotated, the ring gear (321, 330) is also rotated. In this embodiment, the state in which the clutch (410) is fixed to the supporter (310) becomes the washing mode, rinsing mode, or spin-off initial mode, and the state in which the clutch (410) rotates together with the rotor (230) becomes the spin-off mode. And, the state in which the clutch (410) is separated from the supporter (310) and the rotor (230), respectively, becomes the synchronization mode for switching from the spin-off initial mode to the spin-off mode. We will examine these actions again below.

[0111] For reference, in the washing mode, rinsing mode, and the initial spin mode where spin-drying begins after washing, the weight inside the drum (30) is the weight of the laundry plus the weight of the water for washing, so the drum rotation device (100) needs to operate with a relatively large torque and a slow speed. Conversely, in the spin-drying mode where spin-drying is performed in earnest, the weight inside the drum (30) is the weight of the water, so the drum rotation device (100) needs to operate with a relatively small torque and a fast speed. Additionally, a synchronization mode is added in which the speed of the clutch (410) is synchronized with the speed of the rotor (230) to switch from the initial spin-drying mode to the spin-drying mode. Hereinafter, each of the above states will be referred to as "washing mode," "initial spin-drying mode," "synchronization mode," and "spin-drying mode," and "rinsing mode" will be included in "washing mode."

[0112] The guide plate (321A) is connected to the base plate (321B). The base plate (321B) may be a disc structure constituting the upper part of the first housing (321). A plurality of housing fastening holes (324) may be formed in the base plate (321B). The housing fastening holes (324) are for coupling with the internal gear part (330), and the internal protrusion part (332) of the internal gear part (330) may pass through the housing fastening holes (324). Accordingly, the internal gear part (330) can operate integrally with the ring housing part (320).

[0113] A rotational support member (321C) may protrude from the base plate (321B). The rotational support member (321C) protrudes rearward from the surface of the base plate (321B). The rotational support member (321C) is provided around a central portion that penetrates the base plate (321B). The first support bearing (B1) is in close contact with the inner surface of the rotational support member (321C), and the second support bearing (B2) is in close contact with the outer surface of the rotational support member (321C).

[0114] As described below, the sun gear (340) and the coupling unit (350) rotate as a single unit, and the ring gear (321, 330) may rotate together with the sun gear (340) and the coupling unit (350) (spin mode), but the ring gear (321, 330) may stop without rotating together with the sun gear (340) and the coupling unit (350) (washing mode). Accordingly, the ring gear (321, 330) being stably supported to rotate between the sun gear (340) and the coupling unit (350) through the rotation support member (321C) can increase the operational reliability of the drum rotation device (100).

[0115] The internal gear portion (330) may be formed in a ring shape. The internal gear portion (330) may be coupled to the ring housing portion (320) and rotate integrally with the ring housing portion (320). For this coupling, the internal gear portion (330) may be provided with an internal projection portion (332) that is coupled to the housing fastening hole (324) of the ring housing portion (320). The internal projection portion (332) may protrude axially from the surface of the internal gear portion (330).

[0116] Referring to FIG. 8, an internal gear tooth (335) is provided on the inner surface of the internal gear section (330). The internal gear tooth (335) rotates by engaging with the pinion gear tooth (373) of the pinion gears (370). The pinion gears (370) rotate while the pinion gear tooth (373) and the internal gear tooth (335) are engaged with each other. The pinion gears (370) rotate by (i) engaging with the internal gear section (330, ring gear (321, 330)) in a fixed state (washing mode), or (ii) engaging with the internal gear section (330, ring gear (321, 330)) in a rotating state (spin mode). In this embodiment, the internal gear tooth (335) and the pinion gear tooth (373) may be composed of helical gears. As another example, the internal gear tooth (335) and the pinion gear tooth (373) may be composed of spur gears.

[0117] A sun gear (340) may be placed in the internal space (322). The sun gear (340) may serve as an input shaft. That is, the sun gear (340) can receive the rotational force of the rotor (230). The sun gear (340) rotates integrally with the rotor (230). When the rotor (230) rotates, the sun gear (340) always rotates together with the rotor (230) and can transmit the rotational force to the drum shaft (80) through the gear assembly (300).

[0118] On the outer surface of the body of the sun gear (340), a rotor connection part (341) and a transmission gear part (343) may be provided so as to be spaced apart from each other in the axial direction. The rotor connection part (341) is provided on the outer surface of the body of the sun gear (340) and may be connected to the rotor (230). The rotor connection part (341) may be a spline or a serration. The rotor connection part (341) may be coupled to a center fastening hole (357) formed at the center of the sun gear coupling part (355) to be described later. The rotor connection part (341) is not a gear structure, but is coupled to the sun gear coupling part (355) to allow the sun gear (340) to rotate together with the coupling unit (350).

[0119] The transmission gear unit (343) may be spaced apart from the rotor connection unit (341) along the axial direction of the sun gear (340). The transmission gear unit (343) may mesh with the pinion gear teeth (373) of the pinion gears (370). The transmission gear unit (343) enables the rotation of the sun gear (340) to be connected to the rotation of the pinion gears (370). The transmission gear unit (343) may be formed with a larger diameter than the rotor connection unit (341). In this embodiment, the transmission gear unit (343) has a helical gear structure, but as another example, the transmission gear unit (343) may be composed of spur gears.

[0120] A coupling unit (350) may be coupled to the rotor (230). The coupling unit (350) can be viewed as a component that connects the rotor (230) and the sun gear (340), and optionally connects the rotor (230) and the clutch (410). The coupling unit (350) may include a clutch coupling portion (351) and a sun gear coupling portion (355) coupled to the clutch coupling portion (351). As another example, the clutch coupling portion (351) and the sun gear coupling portion (355) may be provided integrally. As yet another example, the coupling unit (350) may be provided integrally to the rotor body (231), or the sun gear (340) may be directly connected to the rotor body (231).

[0121] Referring to FIG. 8, a coupling gear (352) is provided on the bottom surface of the clutch coupling portion (351). The coupling gear (352) may protrude toward the rear. The coupling gear (352) may engage with or be separated from the clutch gear (417) of the clutch (410) described below. When the coupling gear (352) engages with the clutch gear (417), it becomes a rotating state (spin mode), and when the coupling gear (352) is separated from the clutch gear (417), it becomes a locked state (washing mode / spin initial mode) or a neutral state (synchronization mode).

[0122] At this time, the clutch (410) can be switched from the locked state through the neutral state to the rotating state. In the neutral state, a synchronization mode can be implemented in which the rotational speed of the clutch (410) is synchronized with the rotational speed of the rotor (230). Here, the synchronization mode includes a first synchronization mode and a second synchronization mode. In the first synchronization mode, the rotor (230) rotates without shifting, and the clutch (410) is moved by the clutch drive device (400) to switch from the locked state to the neutral state. In the second synchronization mode, the rotor (230) is decelerated, and the clutch (410) is accelerated by the deceleration of the rotor (230).

[0123] When the speeds of the clutch (410) and the rotor (230) are synchronized through the second synchronization mode, the clutch (410) can move toward the rotor (230) and be coupled to the coupling unit (350) of the rotor (230). At this time, the clutch gear (417) of the clutch (410) and the coupling gear (352) of the coupling unit (350) include an inclined structure so that the gears can be aligned between the clutch (410) and the coupling unit (350) in the synchronization mode. This structure will be described below.

[0124] A fastening hole (353A) is opened at the center of the clutch coupling part (351), so that the sun gear coupling part (355) can be positioned therein. The clutch coupling part (351) may be provided with a plurality of fixing protrusions (354) surrounding the fastening hole (353A). The fixing protrusions (354) can be inserted into the coupling hole (235) of the rotor (230) to allow the coupling unit (350), including the clutch coupling part (351), to rotate together with the rotor (230).

[0125] A coupling groove (353B, see FIG. 8) recessed from the inner surface of the fastening hole (353A) may be formed in the clutch coupling portion (351). A coupling protrusion (358) of the sun gear coupling portion (355) is fitted into the coupling groove (353B), so that the clutch coupling portion (351) and the sun gear coupling portion (355) can rotate together.

[0126] A coupling groove (356) may be formed in the center of the above-mentioned sun gear coupling portion (355). The coupling groove (356) is open to the front, and the second support bearing (B2) may be disposed inside the coupling groove (356). The second support bearing (B2) is disposed between the inner surface of the coupling groove (356) and the rotational support portion (321C) of the ring gear (321, 330) to assist in the relative rotation of the coupling unit (350) and the ring gear (321, 330).

[0127] A center fastening hole (357) may be formed in the center of the sun gear coupling part (355). A spline or serration may be formed around the inner periphery of the center fastening hole (357). A part of the sun gear (340) may be inserted into and fixed in the center fastening hole (357). More precisely, the rotor connecting part (341) of the sun gear (340) may be inserted into the center fastening hole (357) so that the sun gear (340) and the sun gear coupling part (355) can be coupled. Accordingly, the sun gear (340) and the coupling unit (350) may rotate or stop simultaneously.

[0128] A carrier (360) is disposed in the internal space (322). The carrier (360) supports the rotation of the pinion gears (370) and can rotate along with the pinion gears (370). More precisely, the carrier (360) can rotate in conjunction with the orbital motion of the pinion gears (370). The carrier (360) is equipped with an output section (363) so that the carrier (360) rotates the drum shaft (80). That is, the result of the rotational motion of the gear assembly (300) can be seen as being transmitted to the drum shaft (80) through the carrier (360).

[0129] Looking at the structure of the carrier (360), the carrier (360) includes a carrier body (361) and a carrier cover (365). The carrier body (361) is positioned so as to be spaced forward of the carrier cover (365) with the pinion gears (370) in between. The output section (363) protrudes from the carrier body (361). A spline or serration is formed on the output section (363) so that it can be coupled to the shaft coupling groove (83) of the drum shaft (80). A spline or serration may also be formed on the shaft coupling groove (83).

[0130] In the carrier body (361) and the carrier cover (365), shaft support holes (362, 367) may be formed at corresponding positions. Both ends of pinion shafts (372), which serve as the rotational axes of the pinion gears (370), may be fitted into the shaft support holes (362, 367). In this embodiment, since a total of four pinion gears (370) are provided in the gear assembly (300), the shaft support holes (362, 367) may also be configured in four pairs. In FIGS. 7 and 8, the reference numeral SP represents a spacer, and the spacer (SP) is positioned between the surface of the sun gear (340) and the surface of the carrier body (361) to facilitate the smooth rotation of the sun gear (340). The spacer (SP) may be omitted.

[0131] Looking at the pinion gears (370), the pinion gears (370) are arranged to surround the sun gear (340). The pinion gears (370) rotate in mesh with the sun gear (340) and the internal gear section (330). More precisely, the pinion gears (370) are positioned between the outer surface of the sun gear (340) and the inner surface of the internal gear section (330), so that the rotational force input through the sun gear (340) is output to the internal gear section (330). If the internal gear section (330) is fixed by the clutch (410), the pinion gears (370) can rotate and simultaneously orbit the internal gear section (330). Conversely, if the internal gear unit (330) is rotated together with the clutch (410), the pinion gears (370) do not rotate but revolve around the sun gear (340) and rotate together with the internal gear unit (330).

[0132] Pinion gear teeth (373) are provided on the surface of the pinion gears (370). The pinion gear teeth (373) mesh with the internal gear teeth (335). In this embodiment, the pinion gear teeth (373) are composed of helical gears. This allows for a reduction in noise generated during gear operation.

[0133] Looking at the bearings that assist in the rotation of the gear assembly (300), the bearings may include the first support bearing (B1), the second support bearing (B2), and the output bearing (B3) described above. The first support bearing (B1) may be positioned between the outer surface of the sun gear (340) and the inner surface of the rotation support part (321C). The second support bearing (B2) has a larger radius than the first support bearing (B1). The second support bearing (B2) may be positioned to surround the outside of the first support bearing (B1). The output bearing (B3) may be positioned between the outer surface of the drum shaft (80) and the second housing (325) of the ring housing part (320).

[0134] For reference, the two drive bearings (B4, B5) shown in FIGS. 4 to 6 are positioned between the drum shaft (80) and the tub (50) to help the drum shaft (80) rotate relative to the tub (50). The first drive bearings (B4) and the second drive bearings (B5) constituting the drive bearings (B4, B5) are spaced apart from each other in the axial direction of the drum shaft (80).

[0135] Next, we will examine the clutch (410) and the clutch drive device (400) that drives the clutch (410). The clutch drive device (400) may be fixed to the supporter (310). The clutch drive device (400) may move the clutch (410) back and forth while fixed. The clutch drive device (400) is equipped with a separate drive motor (not shown) and internal gears (not shown), so that the clutch (410) can be moved by the driving force of the drive motor.

[0136] The clutch drive device (400) may include a drive module (401). The drive module (401) may house a drive motor and internal gears constituting the clutch drive device (400). The internal gears provided inside the drive module (401) reduce the rotation of the drive motor to generate a driving force that moves the clutch lever (420) in a straight line. The drive motor may be configured as a step motor.

[0137] Referring to FIG. 8, the clutch drive device (400) may be equipped with a pinion part (405). The pinion part (405) is connected to the internal gears and rotates. The pinion part (405) engages with a rack part (430) provided on the clutch lever (420) to move the rack part (430) in a straight line. The pinion part (405) is positioned on the opposite side of the gear assembly (300), that is, on the front side, relative to the supporter (310).

[0138] Looking at the clutch (410), the clutch (410) is approximately ring-shaped. The clutch (410) can surround the gear assembly (300). The clutch (410) can move back and forth while surrounding the gear assembly (300). Since the clutch (410) is engaged with the clutch lever (420), it moves together with the clutch lever (420).

[0139] A lever coupling portion (411) that is relatively recessed toward the center may be provided on the outer surface of the clutch (410). The clutch lever (420) may grasp the lever coupling portion (411) and move the clutch (410). As another example, a structure may be provided in which the lever coupling portion (411) protrudes and is recessed into the clutch lever (420).

[0140] A sliding tooth (413) is provided on the inner surface of the clutch (410). The sliding tooth (413) may be a toothed structure extending from the inner surface of the clutch (410) in the direction of movement of the clutch (410). A guide tooth (323) provided on the outer surface of the ring housing part (320) engages with the sliding tooth (413). While engaged with the guide tooth (323), the sliding tooth (413) can move only in a straight line in the forward and backward directions without rotating.

[0141] A locking projection (415) may be provided at one end of the clutch (410). The locking projection (415) is coupled to the locking portion (315) of the supporter (310). When the locking projection (415) engages with the locking portion (315), the clutch (410) becomes unable to rotate. The locking projection (415) may protrude forward from the surface of the clutch (410), that is, toward the rear of the tub (50).

[0142] A clutch gear (417) may be provided at the other end of the clutch (410). The clutch gear (417) engages with the coupling gear (352) of the clutch engagement part (351) when the clutch (410) moves backward. When the clutch (410) is released from the locking part (315) and engages with the coupling gear (352), it rotates together with the rotor (230). Accordingly, the ring gear (321, 330) coupled to the clutch (410) can also rotate together.

[0143] The clutch gear (417) may extend in an inclined direction along the circumferential direction of the clutch (410). More precisely, the clutch gear (417) has a shape that is inclined downward in one direction along the circumferential direction of the clutch (410). This shape allows the clutch gear (417) to stably engage with the coupling gear (352) even when the clutch (410) is rotating. This structure will be explained again below.

[0144] Meanwhile, the clutch (410) can be moved linearly by the clutch lever (420). The clutch lever (420) can be viewed as part of the clutch drive unit (400). The clutch lever (420) moves the clutch (410) while moving by the motor (200) of the clutch drive unit (400). The clutch lever (420) can surround the gear assembly (300). The clutch lever (420) can be moved forward and backward while surrounding the gear assembly (300). Since the clutch lever (420) holds the clutch (410), the clutch (410) moves together with the clutch lever (420).

[0145] The clutch lever (420) may be provided with a lever arm (425). The lever arm (425) is coupled to the lever coupling portion (411) of the clutch (410). The lever arm (425) may be configured to grip the lever coupling portion (411). In this embodiment, the lever arm (425) is configured as a pair, and the pair of lever arms (425) may be extended in a roughly semi-circular shape.

[0146] The clutch lever (420) may be equipped with a rack portion (430). The rack portion (430) engages with the pinion portion (405) to convert the rotational motion of the drive motor equipped in the clutch drive device (400) into linear motion. It can be seen that the drive gears composed of the rack portion (430) and the pinion portion (405) move the clutch (410) in a linear motion.

[0147] Next, we will describe the structure in which the clutch gear (417) and the coupling gear (352) mesh with each other. First, looking at the gear structure of the clutch (410), the sliding tooth (413) is provided on the inner surface of the clutch (410). The sliding tooth (413) meshes with the guide tooth (323) of the ring housing part (320), allowing the clutch (410) to move back and forth along the guide tooth (323). The sliding tooth (413) can be seen as being positioned between the locking projection (415) and the clutch gear (417).

[0148] The clutch gear (417) protrudes from the surface of the clutch (410) in the direction of the coupling gear (352), i.e., rearward. The clutch gear (417) may be provided continuously or discontinuously along the circumferential direction of the clutch (410) on the surface of the clutch (410). In this embodiment, the clutch gear (417) is provided continuously along the circumferential direction of the clutch (410).

[0149] The clutch gear (417) is provided on the opposite side of the locking projection (415). The locking projection (415) faces forward, and the clutch gear (417) faces backward. As the clutch (410) moves along the side of the ring housing (320), the locking projection (415) may be fixed by being caught on the locking portion (315) of the supporter (310), or the clutch gear (417) may be engaged with the coupling gear (352) of the clutch coupling portion (351). In addition, as previously described, the clutch (410) may be spaced apart from the locking portion (315) and the coupling gear (352) to have a neutral state.

[0150] The clutch gear (417) has a structure corresponding to the coupling gear (352). Since the clutch gear (417) meshes with the coupling gear (352), the clutch gear (417) has a structure corresponding to the coupling gear (352). Below, the structure of the clutch gear (417) will be described.

[0151] Referring to FIG. 9, the clutch gear (417) includes a clutch inclined portion (417A) in which the axial height gradually decreases along the circumferential direction of the clutch (410). The clutch gear (417) includes a first clutch engaging portion (417B1) and a second clutch engaging portion (417B2) that are respectively provided at both ends of the clutch inclined portion (417A) and extend in the axial direction. The clutch inclined portion (417A) can align the clutch gear (417) and the coupling gear (352) when the clutch gear (417) and the coupling gear (352) are engaged with each other. The first clutch engaging portion (417B1) and the second clutch engaging portion (417B2) can enable the clutch gear (417) and the coupling gear (352) to be supported circumferentially by each other.

[0152] In this embodiment, the clutch inclined portion (417A) includes a first clutch inclined portion (417A1) and a second clutch inclined portion (417A2). A second clutch engaging portion (417B2) may be provided between the first clutch inclined portion (417A1) and the second clutch inclined portion (417A2). That is, the first clutch engaging portion (417B1) and the second clutch engaging portion (417B2) are provided on each side of the first clutch inclined portion (417A1) with respect to the first clutch inclined portion (417A1). Here, the first clutch engaging portion (417B1) becomes a part that receives the rotational force of the coupling unit (350) when the rotor (230) rotates. More precisely, the first coupling engagement portion (352B1) of the coupling gear (352) can rotate the clutch (410) by pushing the first clutch engagement portion (417B1) of the clutch gear (417) in a circumferential direction.

[0153] The height of the clutch inclined portion (417A) protruding toward the rotor (230) along the circumferential direction of the clutch (410) can gradually decrease. The clutch inclined portion (417A) can be formed such that the surface facing the coupling gear (352) from the clutch gear (417) gradually decreases in height along the circumferential direction. The clutch inclined portion (417A) has a shape corresponding to the coupling inclined portion (352A) of the coupling gear (352). That is, the clutch inclined portion (417A) can form an inclined surface that is in close contact with the coupling inclined surface.

[0154] In this way, when the clutch inclined portion (417A) has an inclined structure, the clutch (410) moves backward (in the direction of arrow ① in FIG. 16) and the clutch gear (417) and the coupling gear (352) engage, the clutch inclined portion (417A) and the coupling inclined surface (352a) naturally slide against each other, and the clutch (410) can be guided in a direction to be in close contact with the clutch coupling portion (351).

[0155] More precisely, the clutch inclined portion (417A) is formed to be inclined downward in the direction in which the clutch gear (417) rotates while engaging with the coupling gear (352) (direction of arrow ① in FIG. 12). Accordingly, when the clutch inclined portion (417A) comes into contact with the coupling inclined portion (352A), the clutch (410) can naturally slide in the direction of rotation. In this embodiment, the clutch (410) engages with the clutch coupling portion (351) in a rotating state rather than a stopped state, and thus the inclined structure of the clutch inclined portion (417A) and the coupling inclined portion (352A) can align them so that the rotating clutch (410) engages accurately with the clutch coupling portion (351).

[0156] On the other hand, the clutch engaging portion (417B) has a steeper angle of inclination than the clutch inclined portion (417A). The clutch engaging portion (417B) can be positioned in a direction parallel to the axial direction, which is the direction of movement of the clutch (410). As another example, the clutch engaging portion (417B) may have an angle of inclination such that it is angled from the direction of movement of the clutch (410). The clutch engaging portion (417B) may have an angle of inclination corresponding to the coupling engaging portion (352B) of the clutch coupling portion (351).

[0157] The clutch engaging portion (417B) is the part where external force is concentrated when the clutch (410) rotates together with the clutch engaging portion (351). Therefore, the clutch engaging portion (417B) needs to support the engaged state between the clutch (410) and the clutch engaging portion (351) so that the clutch (410) does not detach from the clutch engaging portion (351). To this end, the clutch engaging portion (417B) can be mutually supported by making surface contact with the coupling engaging portion (352B) of the coupling gear (352). In this embodiment, the clutch engaging portion (417B) includes a first clutch engaging portion (417B1) and a second clutch engaging portion (417B2), and this structure will be explained again below.

[0158] Referring to FIG. 10, the shape of the clutch gear (417) of the clutch (410) is illustrated. As can be seen, the clutch engaging portion (417B) and the clutch inclined portion (417A) are arranged continuously along the circumferential direction on the surface of the clutch (410). More precisely, the clutch gear (417) includes a first clutch engaging portion (417B1), a first clutch inclined portion (417A1), a second clutch engaging portion (417B2), and a second clutch inclined portion (417A2), and is configured so that they are repeated continuously. That is, in this embodiment, two clutch inclined portions (417A) and two clutch engaging portions (417B) form a single clutch gear tooth.

[0159] This shape can be repeated in the circumferential direction to form the clutch gear (417). As a result, the clutch gear (417) may have a structure that is asymmetrical on both sides with respect to the axial direction. More precisely, the clutch gear (417) may be asymmetrical on the left and right sides with respect to the top part (TL2).

[0160] Likewise, the coupling gear (352) is also arranged continuously along the circumferential direction of the clutch engagement portion (351). The coupling gear (352) includes a first coupling engagement portion (352B1), a first coupling inclined portion (352A1), a second coupling engagement portion (352B2), and a second coupling inclined portion (352A2), and is configured so that these are repeated continuously. That is, in this embodiment, two clutch inclined portions (352A) and two clutch engagement portions (352B) form a single coupling gear tooth. Accordingly, the coupling gear (352) can also be asymmetrical with respect to the top portion (TL1).

[0161] Looking at FIG. 11, the clutch coupling part (351) and the clutch (410) are engaged with each other. In this state, when the clutch coupling part (351) rotates clockwise (arrow ① direction) along the rotor (230), the clutch (410) also rotates in the same direction (arrow ② direction). At this time, the rotational force of the clutch coupling part (351) can be concentrated on the part where the first clutch engaging part (417B1) of the clutch gear (417) and the first coupling engaging part (352B1) of the coupling gear (352) are engaged with each other.

[0162] Referring to FIG. 12, a line extending along the first support surface (SS1) formed by the interlocking portion of the first clutch engagement part (417B1) of the clutch gear (417) and the first coupling engagement part (352B1) of the coupling gear (352) is represented as SL1. This first support surface (SS1) becomes the contact surface where the clutch engagement part (351) presses the clutch (410) when the clutch engagement part (351) rotates in the direction of arrow ①. The clutch (410) pressed on the first support surface (SS1) rotates along the clutch engagement part (351) in the same direction, that is, in the direction of arrow ②.

[0163] At this time, when the rotor (230) rapidly decelerates, the coupling gear (352) coupled to the rotor (230) also rapidly decelerates. On the other hand, since the clutch (410) continues to rotate in the same direction (arrow ② direction) due to rotational inertia, the direction of acceleration of the clutch coupling part (351) (arrow ③ direction) and the direction of rotation of the clutch (410) (arrow ② direction) may be opposite to each other. In this case, there is a risk that the coupling gear (352) and the clutch gear (417) will be separated axially as the inclined part (352A) of the coupling gear (352) crosses over the inclined part (417A) of the clutch gear (417). However, in this embodiment, the second clutch engaging portion (417B2) of the clutch gear (417) and the second coupling engaging portion (352B2) of the coupling gear (352) engage with each other to form a second support surface (SS2), thereby allowing for support in the reverse rotation direction. Accordingly, the phenomenon in which the inclined portion (352A) of the coupling gear (352) runs over the inclined portion (417A) of the clutch gear (417) is prevented. SL2 represents a line extended along the second support surface (SS2).

[0164] As shown in FIG. 12, the extension line (SL1) extended along the first support surface (SS1) and the extension line (SL2) extended along the second support surface (SS2) may be parallel to each other in the axial direction. The first support surface (SS1) and the second support surface (SS2) are spaced apart in the circumferential direction (left-right direction in FIG. 12) of the clutch (410) so that they can support the clutch gear (417) and the coupling gear (352) in opposite directions relative to the circumferential direction. The first support surface (SS1) can support the clutch gear (417) and the coupling gear (352) in the acceleration direction (arrow ① direction) of the clutch coupling part (351). The second support surface (SS2) can support the clutch gear (417) and the coupling gear (352) in the deceleration direction (arrow ③ direction) of the clutch coupling part (351). As a result, the clutch gear (417) and the coupling gear (352) can be supported by each other in both directions with respect to the circumferential direction.

[0165] The first clutch inclined portion (417A1) of the clutch gear (417) and the second coupling inclined portion (352A2) of the coupling gear (352) can be in axial contact with each other to form a first contact surface (IS1). At the same time, the second clutch inclined portion (417A2) of the clutch gear (417) and the first coupling inclined portion (352A1) of the coupling gear (352) can be in axial contact with each other to form a second contact surface (IS2). By having different axial heights and forming multiple contact surfaces, the two gears (352, 417) are stably coupled to each other.

[0166] Referring to FIG. 13, the coupling gear (352) of the clutch coupling part (351) that meshes with the clutch gear (417) is shown together with the clutch gear (417). FIG. 13 shows the state before the clutch gear (417) meshes with the coupling gear (352). As can be seen, the clutch inclined part (417A) of the clutch gear (417) may face the coupling inclined part (352A) of the coupling gear (352). Even if the clutch inclined part (417A) is not precisely aligned with the coupling inclined part (352A), the angle of inclination of the two inclined parts (352A, 417A) can induce them to take an accurate position relative to each other.

[0167] With reference to FIG. 13, the structure of the clutch gear (417) will be examined in more detail. In FIG. 13, P2 represents a range of clutch gear teeth constituting the clutch gear (417). At both ends of the clutch gear teeth constituting the clutch gear (417), a top portion (TL2) and a bottom portion (BL2) are respectively provided. The top portion (TL2) is the part that protrudes highest in the axial direction, and the bottom portion (BL2) is the part that is lowest in the axial direction.

[0168] At this time, the axial height of the clutch inclined portion (417A) may gradually decrease from the top portion (TL2) toward the bottom portion (BL2). The first clutch inclined portion (417A1) constituting this embodiment may gradually decrease from the top portion (TL2) toward the bottom portion (BL2). The second clutch inclined portion (417A2) constituting this embodiment may also gradually decrease from the top portion (TL2) toward the bottom portion (BL2). By forming an inclined surface protruding toward the rotor (230), the second clutch inclined portion (417A2) can reduce impact during the engagement process between the clutch (410) and the clutch coupling portion (351).

[0169] The first clutch engaging portion (417B1) can connect the top portion (TL2) and the bottom portion (BL2) of an adjacent gear tooth. The first clutch engaging portion (417B1) can connect the upper portion, which has the highest axial height of the first clutch inclined portion (417A), and the lower portion, which has the lowest axial height of an adjacent clutch inclined portion (417A), thereby forming a step between them.

[0170] The first clutch engaging portion (417B1) may have a higher axial height than the second clutch engaging portion (417B2). In this embodiment, the upper end of the first clutch engaging portion (417B1) is formed on the top portion (TL2). Since the first clutch engaging portion (417B1) is a part that receives the rotational force of the rotor (230), it is preferable for it to have a larger surface area than the second clutch engaging portion (417B2). Although not illustrated, the top portion (TL2), that is, the upper end of the first clutch engaging portion (417B1), may be formed as a curved surface.

[0171] The second clutch engaging portion (417B2) may be provided between the clutch inclined portion (417A) and the bottom portion (BL2). Referring to FIG. 14, the second clutch engaging portion (417B2) may form a step by connecting a first end portion (417B2') which has an axial height lower than the upper end portion of the clutch inclined portion (417A) and a second end portion (417B2'') which has an axial height lower than the first end portion (417B2') and an axial height higher than the lower end portion of the clutch inclined portion (417A). In this embodiment, the second clutch engaging portion (417B2) is provided between the first clutch inclined portion (417A1) and the bottom portion (BL2). In this way, a step structure can be formed between the first clutch inclined portion (417A1) and the second clutch inclined portion (417A2). It may also be said that inclined portions (417A1, 417A2) are provided on each side based on the step structure.

[0172] The second clutch engaging portion (417B2) may be provided between one end and the other end of the clutch inclined portion (417A). Here, the one end of the clutch inclined portion (417A) may be the top portion (TL2), which is the upper end of the first clutch inclined portion (417A1). The other end of the clutch inclined portion (417A) may be the bottom portion (BL2), which is the lower end of the second clutch inclined portion (417A2). Therefore, the second clutch engaging portion (417B2) can be considered to be provided between the top portion (TL2) and the bottom portion (BL2).

[0173] In FIG. 13, P1 represents a range of one coupling gear tooth constituting the coupling gear (352). At both ends of one coupling gear tooth constituting the coupling gear (352), a top portion (TL1) and a bottom portion (BL1) are respectively provided. The top portion (TL1) is the part that protrudes highest in the axial direction, and the bottom portion (BL1) is the part that is lowest in the axial direction. At this time, the axial height of the coupling inclined portion (352A) can gradually decrease from the top portion (TL1) toward the bottom portion (BL1). The first coupling inclined portion (352A1) constituting the present embodiment can gradually decrease from the top portion (TL1) toward the bottom portion (BL1). The second coupling inclined portion (352A2) constituting the present embodiment can also gradually decrease from the top portion (TL1) toward the bottom portion (BL1). Since the structure of the coupling gear (352) is symmetrical to the structure of the clutch gear (417), the detailed description of the structure of the coupling gear (352) will be replaced by the description of the clutch gear (417).

[0174] Referring to FIG. 14, the clutch gear (417) and the coupling gear (352) are shown engaged with each other. As can be seen, with respect to a reference line extending in the circumferential direction of the clutch (410), the second clutch inclined portion (417A2) may have an angle of inclination smaller than or equal to that of the first clutch inclined portion (417A1). More precisely, the angle of inclination (A) of the first clutch inclined portion (417A1) may be greater than or equal to the angle of inclination (B) of the second clutch inclined portion (417A2). The first clutch inclined portion (417A1) performs alignment between the clutch (410) and the coupling unit (350), and for faster alignment, the angle of inclination (A) of the first clutch inclined portion (417A1) may be formed larger.

[0175] The two clutch inclined sections (417A) may have different axial heights relative to the second clutch engaging section (417B2). For example, the axial height of the first clutch inclined section (417A1) may be higher than the axial height of the second clutch inclined section (417A2). As another example, the axial height of the first clutch inclined section (417A1) and the axial height of the second clutch inclined section (417A2) may be the same.

[0176] Meanwhile, the inclination angle (C) of the second clutch engaging part (417B2) can be formed to be 80 to 90 degrees based on a reference line extending in the circumferential direction of the clutch (410). If the inclination angle (C) of the second clutch engaging part (417B2) is less than 80 degrees, when a large external force is applied between the clutch (410) and the coupling unit (350), the inclined part (352A) of the coupling gear (352) may run over the inclined part (417A) of the clutch gear (417). Of course, although the pinion part (405) of the clutch driving device (400) is engaged with the rack part (430), a large external force sufficient to overcome such force may be applied, so it is preferable that the inclination angle (C) of the second clutch engaging part (417B2) be greater than 80 degrees. Conversely, if the inclination angle (C) of the second clutch engaging part (417B2) is greater than 90 degrees, a reverse gradient structure is formed between the clutch gear (417) and the coupling gear (352), so axial coupling cannot be smoothly achieved. In this embodiment, the first clutch engaging part (417B1) and the second clutch engaging part (417B2) are provided in a direction perpendicular to the circumferential direction of the clutch (410).

[0177] Referring to FIG. 15, the heights of the clutch inclined portion (417A) and the clutch engaging portion (417B) constituting the clutch gear (417) are shown. The axial height (m1-h1) of the first clutch engaging portion (417B1) may be formed to be higher than the axial height (H3A-H3B) of the second clutch engaging portion (417B2). More precisely, in this embodiment, the axial height (m1-h1) of the first clutch engaging portion (417B1) is equal to the sum of the axial height (m1-H3A) of the first clutch inclined portion (417A1), the axial height (H3B-h1) of the second clutch inclined portion (417A2), and the axial height (H3A-H3B) of the second clutch engaging portion (417B2).

[0178] The two clutch inclined sections (417A) may have different axial heights relative to the clutch engaging section (417B). In FIG. 15, the axial height (m1-H3A) of the first clutch inclined section (417A1) may be higher than the axial height (H3B-h1) of the second clutch inclined section (417A2). In this way, during the process of coupling the clutch (410) and the coupling unit (350), the first clutch inclined section (417A1) may have a longer first contact surface (IS1, see FIG. 12) with the first coupling inclined section (352A1).

[0179] The circumferential length (P2A) between the top portion (TL2) and the second clutch engaging portion (417B2) may be longer than or equal to the circumferential length (P2B) between the second clutch engaging portion (417B2) and the bottom portion (BL2). In this way, during the process of coupling the clutch (410) and the coupling unit (350), the sliding guide surface of the first clutch inclined portion (417A1) with the first coupling inclined portion (352A1) can be secured to be long.

[0180] FIGS. 16 to 19 sequentially show the process of the clutch (410) and the clutch coupling part (351) being coupled to each other. The clutch (410) can be moved backward (in the direction of arrow ① in FIG. 16) by the clutch driving device (400). At this time, the rotational speeds of the clutch (410) and the clutch coupling part (351) are synchronized. Since the synchronization process has been explained previously, the explanation will be omitted. Of course, the rotational speeds of the clutch (410) and the clutch coupling part (351) may not be exactly the same, but the clutch inclined part (417A) and the coupling inclined part (352A) can compensate for this.

[0181] Looking at FIG. 16, the clutch gear (417) and the coupling gear (352) are axially separated from each other but are not precisely aligned. Here, alignment means that the first coupling inclined portion (352A1) of the coupling gear (352) faces the second clutch inclined portion (417A2) of the clutch gear (417) axially, and at the same time, the second coupling inclined portion (352A2) of the coupling gear (352) faces the first clutch inclined portion (417A1) of the clutch gear (417) axially. FIG. 16 shows the state in which the two gears are not aligned with each other.

[0182] In this state, when the clutch (410) moves backward (in the direction of arrow ① in FIG. 16), the state shown in FIG. 17 is obtained. FIG. 17 shows the state in which the first clutch inclined portion (417A1) of the clutch gear (417) is in contact with the second coupling inclined portion (352A2) of the coupling gear (352). The first clutch inclined portion (417A1) and the second coupling inclined portion (352A2) of the coupling gear (352) may have an inclined contact surface with respect to each other. In this state, when the clutch driving device (400) moves the clutch (410) backward (in the direction of arrow R in FIG. 17), the clutch (410) can rotate and slide diagonally (in the direction of arrow ② in FIG. 17). The direction in which it slides is the same as the direction in which the clutch (410) rotates together with the clutch coupling portion (351). In this process, the coupling gear (352) and the clutch gear (417) are aligned with each other.

[0183] Referring to FIG. 18, the clutch inclined portion (417A) slides along the coupling inclined portion (352A) and aligns with each other. In this state, the clutch (410) moves backward (in the direction of arrow R in FIG. 18), and the gap with the clutch engagement portion (351) decreases. After the clutch (410) rotates (slides) and aligns, it continues to move backward, and the clutch engaging portion (417B) and the coupling inclined portion (352A) move axially while facing each other.

[0184] Looking at FIG. 19, the clutch (410) and the clutch coupling portion (351) are in complete contact. More precisely, the first coupling inclined portion (352A1) of the coupling gear (352) is in axial contact with the second clutch inclined portion (417A2) of the clutch gear (417), and at the same time, the second coupling inclined portion (352A2) of the coupling gear (352) is in axial contact with the first clutch inclined portion (417A1) of the clutch gear (417). The first coupling engagement portion (352B1) of the coupling gear (352) faces the first clutch (410) engagement portion of the clutch gear (417) in a circumferential direction, and at the same time, the second coupling engagement portion (352B2) of the coupling gear (352) faces the first clutch engagement portion (417B1) of the clutch gear (417) in a circumferential direction.

[0185] In this state, when the clutch coupling part (351) rotates in the first direction (right direction in FIG. 19) with respect to the circumferential direction, the clutch (410) engaged with the clutch coupling part (351) also rotates together in the first direction. At this time, the rotational force of the clutch coupling part (351) is transmitted to the clutch (410) through the first support surface (SS1, see FIG. 12) between the first coupling engagement part (352B1) of the coupling gear (352) and the first clutch (410) engagement part of the clutch gear (417).

[0186] As the clutch coupling part (351) and the clutch (410) rotate together, the rotor (230) may be decelerated. When the rotor (230) is rapidly decelerated, the clutch coupling part (351) is also rapidly decelerated, but the clutch (410) is decelerated relatively later due to rotational inertia. Accordingly, the direction of acceleration of the clutch coupling part (351) (left direction in FIG. 19) and the direction of rotation of the clutch (410) (right direction in FIG. 19) may be opposite to each other.

[0187] At this time, the second clutch engaging portion (417B2) of the clutch gear (417) and the second coupling engaging portion (352B2) of the coupling gear (352) are supported in a circumferential direction to form a second supporting surface (SS2, see FIG. 12), thereby preventing the inclined portion (352A) of the coupling gear (352) from riding over the inclined portion (417A) of the clutch gear (417). The second coupling engaging portion (352B2) is provided between the top portion (TL1) and the bottom portion (BL1) of the clutch gear (417) to form a step. The step of the second coupling engaging portion (352B2) is in close contact with the step formed by the second clutch engaging portion (417B2) and can be supported in a circumferential direction.

[0188] FIG. 20 illustrates a second embodiment of a clutch gear (417) constituting an embodiment of the present invention. To describe only the structure different from the preceding embodiment, the clutch gear (417) includes one clutch inclined portion (417A) and two clutch engaging portions (417B1, 417B2) respectively provided on both sides of the clutch inclined portion (417A). Among the two clutch engaging portions (417B1, 417B2), the first clutch engaging portion (417B1) receives the rotational force of the clutch coupling portion (351), and the second clutch engaging portion (417B2) can prevent the two gears from separating axially from each other during rapid deceleration of the rotor (230).

[0189] The second clutch engagement portion (417B2) is provided with a clutch seating portion (417C). The clutch seating portion (417C) may extend in the circumferential direction of the clutch (410). Unlike the clutch inclined portion (417A), the clutch seating portion (417C) may not have an inclination angle and may have a horizontal structure in the circumferential direction. The clutch seating portion (417C) may be in close contact with the coupling seating portion (not shown) of the coupling gear (352). It may also be said that the second clutch engagement portion (417B2) is provided between the clutch seating portion (417C) and the clutch inclined portion (417A).

[0190] FIG. 21 illustrates a third embodiment of a clutch gear (417) constituting an embodiment of the present invention. To describe only the structure different from the previous embodiment, the clutch gear (417) is provided with three clutch inclined portions (417A) and three clutch engaging portions (417B), respectively. The clutch engaging portions (417B) are arranged between the three clutch inclined portions (417A) to create a plurality of stepped structures.

[0191] The three clutch inclined sections (417A) include a first clutch inclined section (417A1), a second clutch inclined section (417A2), and a third clutch inclined section (417A3) having different axial heights from each other. At this time, a second clutch engaging section (417B2) is positioned between the first clutch inclined section (417A1) and the second clutch inclined section (417A2). A third clutch engaging section (417B3) is positioned between the second clutch inclined section (417A2) and the third clutch inclined section (417A3).

[0192] The first clutch engaging part (417B1) among the three clutch engaging parts (417B) receives the rotational force of the clutch engaging part (351). The second clutch engaging part (417B2) and the third clutch engaging part (417B3) among the three clutch engaging parts (417B) can each prevent the two gears from separating axially from each other during rapid deceleration of the rotor (230).

[0193] The foregoing description is merely an illustrative explanation of the technical concept of the present invention, and those skilled in the art to which the present invention pertains will be able to make various modifications and variations within the scope of the essential characteristics of the present invention. Accordingly, the embodiments disclosed in the present invention are intended to explain, not limit, the technical concept of the present invention, and the scope of the technical concept of the present invention is not limited by such embodiments. The scope of protection of the present invention shall be interpreted by the claims below, and all technical concepts within an equivalent scope shall be interpreted as being included within the scope of rights of the present invention.

Claims

1. A motor comprising a stator and a rotor that rotates relative to the stator and rotates the motor shaft; A clutch that moves in the axial direction of the motor shaft and is connected to the rotor, and connects the motor and the gear assembly; and A clutch driving device for moving the clutch in the axial direction; comprising The clutch and the rotor are each provided with a clutch gear and a coupling gear that are coupled to each other in the axial direction. The above clutch gear is A clutch inclined portion in which the axial height gradually decreases along the circumferential direction of the above clutch, and A first clutch engaging portion extending in the axial direction from one end of the above-mentioned clutch inclined portion, and A drum rotating device including a second clutch engaging portion provided between one end and the other end of the above-mentioned clutch inclined portion.

2. In claim 1, the clutch inclined portion has a continuously decreasing axial height along the circumferential direction of the clutch, and The first clutch engaging portion is formed by connecting the upper portion, which has the highest axial height of the clutch inclined portion, and the lower portion, which has the lowest axial height of an adjacent clutch inclined portion, to form a step. The drum rotating device in which a step is formed by connecting a first end portion, which has an axial height lower than the upper end portion of the clutch inclined portion, and a second end portion, which has an axial height lower than the first end portion and an axial height higher than the lower end portion.

3. In claim 1, at both ends of one clutch gear tooth constituting the clutch gear, a top portion having the highest axial height and a bottom portion having the lowest axial height are respectively provided, and The above clutch inclined portion gradually decreases in axial height from the top portion toward the bottom portion, and The second clutch engaging part is a drum rotating device provided between the top part and the bottom part.

4. The drum rotating device according to claim 1, wherein the first clutch engaging portion has an axial height higher than the second clutch engaging portion.

5. In claim 1, at both ends of one clutch gear tooth constituting the clutch gear, a top portion having the highest axial height and a bottom portion having the lowest axial height are respectively provided, and The above clutch slope A first clutch inclined portion in which the axial height gradually decreases from the top portion toward the upper end of the second clutch engaging portion; and, A drum rotating device comprising: a second clutch inclined portion in which the axial height gradually decreases from the lower end of the second clutch engaging portion toward the bottom portion.

6. In claim 5, the upper end of the first clutch engaging portion is formed on the top portion, and The lower end of the second clutch inclined portion is a drum rotating device formed in the bottom portion.

7. A drum rotating device according to claim 5, wherein the second clutch inclined portion has an angle of inclination smaller than or equal to the first clutch inclined portion with respect to a reference line extending in the circumferential direction of the clutch.

8. A drum rotating device according to claim 1, wherein two different clutch inclined portions are provided on both sides of the second clutch engaging portion based on the second clutch engaging portion.

9. In claim 8, the two clutch inclined portions are drum rotating devices having different axial heights with respect to the second clutch engaging portion.

10. A drum rotating device according to claim 1, wherein the first clutch engaging portion and the second clutch engaging portion are each provided in a direction perpendicular to the circumferential direction of the clutch.

11. A drum rotating device according to claim 1, wherein the axial height of the second clutch engaging portion is lower than the axial height of the clutch inclined portion.

12. In claim 1, at both ends of one clutch gear tooth constituting the clutch gear, a top portion having the highest axial height and a bottom portion having the lowest axial height are respectively provided, and A drum rotating device in which the circumferential length between the top part and the second clutch engaging part is longer than or equal to the circumferential length between the second clutch engaging part and the bottom part.

13. In Claim 1, one clutch gear tooth constituting the clutch gear The above clutch inclined portion; and The above first clutch engaging part and the above second clutch engaging part; are included, The first clutch engaging part above connects the top part, which has the highest axial height, and the bottom part, which has the lowest axial height of an adjacent clutch gear tooth, and the drum rotating device extending in the axial direction.

14. A drum rotating device according to claim 1, wherein at least one of the boundary between the clutch inclined portion and the second clutch engaging portion and the upper end of the first clutch engaging portion is formed as a curved surface.

15. In Claim 1, the coupling gear teeth constituting the coupling gear A coupling inclined portion guided by the above-mentioned clutch inclined portion; A first coupling engaging portion that is in close contact with the first clutch engaging portion in the circumferential direction of the clutch; and A drum rotating device comprising: a second coupling engaging portion that is in close contact with the second clutch engaging portion in the circumferential direction of the clutch.

16. In claim 1, each end of one coupling gear tooth constituting the coupling gear is provided with a top portion having the highest axial height and a bottom portion having the lowest axial height, respectively. The above coupling gear is The axial height gradually decreases from the top portion toward the bottom portion, and the coupling inclined portion guided by the clutch inclined portion, and It includes a second coupling catch portion provided between the top portion and the bottom portion and extending in the axial direction; The second coupling engaging portion is a drum rotating device that is in close contact with the second clutch engaging portion in the circumferential direction of the clutch.

17. In claim 1, the clutch is switched from a locked state through a neutral state to a rotating state, and A synchronization mode is implemented in which the rotational speed of the clutch is synchronized with the rotational speed of the rotor in the above neutral state, and The above synchronization mode is A first synchronization mode in which the rotor rotates without shifting and the clutch is moved by the clutch drive device to switch from the locked state to the neutral state; and A second synchronization mode in which the rotor is decelerated and the clutch is accelerated by the deceleration of the rotor; is included. When the speeds of the clutch and the rotor are synchronized through the second synchronization mode, the clutch moves toward the rotor and engages with the coupling unit of the rotor. The above coupling gear is a drum rotating device provided in the above coupling unit.

18. In claim 1, the clutch driving device is provided with driving gears that linearly move the clutch in the axial direction, and The above drive gears A pinion part rotated by a drive motor of the above-mentioned clutch drive device; and It includes a rack part that is linked to the pinion part and moves linearly in the axial direction; The above clutch is a drum rotating device coupled to the above rack portion and moving linearly in the axial direction.

19. A motor comprising a stator and a rotor that rotates relative to the stator and rotates the motor shaft; A clutch that moves in the axial direction of the motor shaft and is connected to the rotor, and connects the motor and the gear assembly; and A clutch driving device for moving the clutch in the axial direction; comprising The clutch and the rotor are each provided with a clutch gear and a coupling gear that are coupled to each other in the axial direction. The clutch gear and the coupling gear each have corresponding inclined portions formed therein, and The clutch gear and the coupling gear form a plurality of spaced-apart locking portions along the circumferential direction of the clutch within a single gear tooth that is meshed with each other. The above plurality of locking parts are drum rotating devices having different axial heights.

20. A drum rotating device according to any one of claims 1 to 19; and A clothing processing device comprising: a drum that is rotated by the above-mentioned drum rotation device and has a storage space formed inside.

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