Drum rotating device and laundry treating apparatus including the same

Abstract

The present invention relates to a drum rotating device (100) and a laundry treating apparatus including the same. The drum rotating device (100) of the present invention can include a clutch (410) and a clutch driving device (400) driving the clutch (410). The clutch driving device (400) can include a driving member (450) having a rotation center concentric with a motor shaft (340) and rotated by a driving source (441). At this time, a push member (460) moving in the axial direction in linkage with the rotation of the driving member (450) can move the clutch (410) in the axial direction. As described above, if configured such that the clutch driving device (400) has a rotation center concentric with the motor shaft (340), it is possible to prevent an increase in the radial dimension of the drum rotating device (100) due to the clutch driving device (400).

Description

Technical Field

[0001] This invention relates to a drum rotation device and a garment processing device including the same. Background Technology

[0002] Generally, a garment processing device refers to a device for washing or drying laundry. Such devices include washing machines and dryers. Washing machines, in particular, clean stains on clothes, bedding, and other laundry items through washing, rinsing, and spin-drying processes.

[0003] Recently, various types of washing machines have been commercialized. These include upright washing machines, which rotate the swirl tub containing laundry about a longitudinal axis, and front-loading washing machines, which rotate about a horizontal or inclined axis. All such washing machines are driven by a motor.

[0004] Front-loading washing machines perform a series of washing processes, including washing, rinsing, and spin-drying, by rotating the drum that holds the laundry. During the washing or rinsing process, which involves rotating laundry containing a large amount of water, a low-speed, high-torque rotational force is required. Conversely, during the spin-drying process, which involves rotating the laundry to reduce it to a nearly dry state, a high-speed, low-torque rotational force is required.

[0005] As described above, the drum drive unit that drives a washing machine needs to provide various rotational forces and speeds depending on the drive mode. Therefore, a reducer and a clutch are employed in the drum drive unit. For example, referring to Korean Patent Publication 10-2020-0089604 (Prior Patent 1), Korean Patent Publication 10-2023-0090484 (Prior Patent 2), and Korean Patent Grant 10-1920812 (Prior Patent 3), a technique is disclosed that reduces the speed of the motor by arranging a plurality of gears, such as a planetary gear assembly, between the motor and the output shaft. The clutch can change the torque and speed of the output shaft coupled to the rotating shaft of the rotating slot by controlling the drive of a portion of the plurality of gears.

[0006] However, based on the structure of the aforementioned existing patents, the clutch power unit (actuator) for driving the clutch is also housed inside the roller drive device. To ensure sufficient space, the clutch power unit is positioned radially offset from the center of the roller drive device. For example, the clutch power unit is positioned radially outward from the inner circumferential surface of the motor stator. Therefore, there is a problem that the overall volume of the roller drive device increases due to the space required to house the clutch power unit.

[0007] Furthermore, in existing rotary drum devices, the multiple clutch power units are separated from the couplers, necessitating structures such as levers for transmitting power between them. Existing clutch power units have a structure where the lever rotates to move the coupler linearly. This structure suffers from the disadvantage that the driving directions of the lever and the coupler are different, requiring a large torque to drive the coupler and thus reducing driving efficiency. Additionally, the different driving directions of the clutch power unit and the coupler also reduce the reliability of the coupler's operation.

[0008] Furthermore, if the power transmission path of the clutch power unit becomes longer, the structure for transmitting power from the clutch power unit to the coupler becomes more complex, and the number of parts increases. In addition, if the number of parts increases as described above, the durability of the clutch power unit also decreases.

[0009] Furthermore, the power components for the clutch are located separately from the motor and gears, which leads to a decrease in the assembly efficiency and space utilization of the roller rotation device.

[0010] Furthermore, existing roller rotating devices require not only structures for mounting the motor and gears, but also structures for mounting the power unit for the clutch. Therefore, existing roller rotating devices suffer from the disadvantage of increasing the number of components required for mounting and the number of assembly workers. Summary of the Invention

[0011] The problem that the invention aims to solve

[0012] The present invention addresses the problems of the prior art as described above. The object of the present invention is to reduce the overall diameter of the drum rotating device by aligning the clutch drive device along the axial direction of the drum rotating device.

[0013] Another object of the present invention is to make the driving direction of the pusher constituting the clutch drive device the same as the driving direction of the clutch.

[0014] Another objective of the present invention is that the pusher component constituting the clutch drive device moves only linearly along the axial direction, and the drive member that actuates the pusher component rotates only around the motor shaft, thereby achieving duality.

[0015] Another object of the present invention is that the motor mounts the clutch drive device as a medium to the gear assembly (gear cover) without providing additional fixing devices for fixing the motor.

[0016] Technical solutions to the problem

[0017] According to the features of the present invention for achieving the above-mentioned objectives, the drum rotating device of the present invention may include a clutch and a clutch drive device for driving the clutch. The clutch drive device may include a drive member having a rotation center concentric with the motor shaft and rotated by a drive source. In this case, a pusher member that moves along the axial direction in conjunction with the rotation of the drive member can move the clutch along the axial direction. As described above, if the clutch drive device is configured to have a rotation center concentric with the motor shaft, it is possible to prevent an increase in the radial dimension of the drum rotating device due to the clutch drive device.

[0018] Furthermore, the drum rotating device of the present invention may include: an output shaft coupled to the drum; and a motor including a stator and a rotor rotating relative to the stator. The drum rotating device may include a gear assembly that transmits the rotational force of the rotor to the output shaft, the gear assembly including a motor shaft connected to the motor. The drum rotating device may include a clutch that moves axially along the motor shaft and is connected to the rotor, and a clutch drive device that moves the clutch along the axial direction. As described above, the push member of the clutch drive device moves axially in the same direction as the movement of the clutch, thus eliminating the need to transmit the rotational force of the drive source (motor) radially to the push member. Therefore, the structure for power transmission of the clutch drive device can be simplified.

[0019] Additionally, the drive member can be configured in the clutch drive mechanism to limit the movement of the drive member along the axial direction. The push member can be configured in the clutch drive mechanism to limit the relative rotation between the push member and the drive member. In this way, the drive member does not need to perform linear movement, thus the gear shape for linkage with the drive source and the cam shape for moving the push member can be easily implemented.

[0020] Furthermore, the driving member and the pushing member can be configured to be concentric with each other. In this way, the radial dimension of the drum rotating device will not increase due to the clutch drive device, therefore the clutch drive device of the present invention can also be applied to small-sized drum rotating devices.

[0021] Additionally, the drive member and the pusher member can be configured to respectively surround the motor shaft.

[0022] Furthermore, the drive member can be configured to be closer to the motor in the axial direction than the pusher. The drive member can move the pusher in the axial direction away from the motor.

[0023] Furthermore, the drive member and the pusher member can be configured to respectively surround the motor shaft. The drive member and the pusher member can overlap each other radially. This overlapping structure can further reduce the axial length of the clutch drive device, thereby also reducing the axial length of the roller rotation device.

[0024] Furthermore, the clutch, the drive member, and the pusher can be configured to overlap each other radially. The drive member and the pusher can be concentric with each other and respectively surround the motor shaft. The pusher can be guided by the outer peripheral surface of the drive member, thereby moving along the axial direction.

[0025] Furthermore, the stator and the gear assembly can be spaced apart from each other along the axial direction. The clutch drive device can be arranged axially between the stator and the gear assembly. The clutch drive device can be coupled to both the stator and the gear assembly. As described above, the motor can use the clutch drive device as a medium to engage with the gear assembly, eliminating the need for additional structures to secure the motor. Therefore, the number of components used to secure the motor can be reduced, and the motor can be secured together during the installation of the clutch drive device, thus reducing assembly work.

[0026] Furthermore, the diameter of the clutch drive device can be smaller than the diameter of the gear assembly, and the diameter of the clutch drive device can be smaller than the diameter of the motor.

[0027] Additionally, one of the driving member and the pushing member may be provided with a guide cam portion whose axial length varies circumferentially. The other of the driving member and the pushing member may be provided with a lifting guide portion guided by the guide cam portion. If the driving member rotates, the lifting guide portion can move along the guide cam portion in the axial direction.

[0028] Furthermore, the drive member may be provided with a drive cam whose axial length varies along the circumference of the drive member. The push member may be provided with a driven cam, which is guided by the drive cam, and whose axial length varies along the circumference of the push member. If the drive member rotates, the driven cam can move along the drive cam in the axial direction. With this structure, the drive cam and the driven cam can switch the rotational motion of the drive member to the linear motion of the push member while they are in surface contact with each other. This not only improves the operational reliability of the clutch drive device but also reduces the load on the drive source by adjusting the tilt angle of the cam structure.

[0029] Additionally, the drive cam may have a push drive portion having a first tilt angle relative to the circumferential direction of the drive member. The driven cam may have a disengagement drive portion having the same tilt angle relative to the circumferential direction of the push member as the first tilt angle. The push drive portion and the disengagement drive portion may be configured to face each other.

[0030] Furthermore, the gear assembly may include: a gear housing with an internal mounting space; and a plurality of gears disposed in the mounting space and rotate in conjunction with the motor shaft. In this case, the clutch drive device can be fixed to the gear housing in a manner that surrounds the motor shaft.

[0031] Additionally, the clutch drive device may include a drive housing with an internal operating space where the drive source is disposed. The drive member may be disposed within the operating space, and the drive member can rotate under the rotational force of the drive source. At least a portion of the push member may be disposed within the operating space and move along the axial direction.

[0032] Furthermore, a portion of the pusher can move in and out of the inner and outer sides of the action space along the axial direction.

[0033] Additionally, the drive housing may be provided with an anti-rotation portion that interferes with the push member in the circumferential direction. The anti-rotation portion may be continuously formed along the moving direction of the push member.

[0034] Furthermore, the drive housing may have a radially recessed anti-rotation groove. The push member may have an anti-rotation protrusion that protrudes radially and inserts into the anti-rotation groove. The anti-rotation groove may extend along the moving direction of the push member.

[0035] Additionally, the drive housing may have an opening for the pusher to move in and out. The radius of the pusher moving hole may be smaller than the radial distance between the center of the pusher and the end of the anti-rotation protrusion.

[0036] Furthermore, the drive source can be configured to be radially spaced from both the drive member and the push member of the clutch drive device. The radial distance between the rotation center of the drive member and the drive source can be shorter than the radial distance from the rotation center of the gear assembly to its radial end. The radial distance from the rotation center of the drive member to the drive source can be shorter than the radial distance from the rotation center of the motor to its edge.

[0037] Additionally, the driving component may include: a ring-shaped driving body; and a driving gear, disposed on the surface of the driving body along the circumference of the driving body, meshing with the driving source to rotate. In this case, a driving cam may be disposed on the surface of the driving body along the circumference of the driving component, and the axial distance of the driving cam may vary along the circumference. In this way, the driving component can rotate continuously in one direction and cause the pusher to rise and fall. Therefore, the driving source that actuates the driving component can also rotate only in one direction, and the operating mechanism of the clutch drive device can be simply implemented.

[0038] Furthermore, the drive gear and the drive cam can be respectively disposed on different surfaces of the drive body.

[0039] Furthermore, in the roller rotating device, the radial distance from the rotation center of the driving member to the driving gear is greater than the radial distance from the rotation center of the driving member to the driving cam.

[0040] Furthermore, a guide wall may be provided along the circumference of the driving member. A driving cam may be provided on the surface of the guide wall, the axial distance of the driving cam varying along the circumference of the guide wall. The push member may be configured to surround the guide wall. A driven cam corresponding to the driving cam may be provided on the outer peripheral surface of the push member facing the guide wall.

[0041] Furthermore, the pusher and the clutch may each have a push surface and a contact support portion facing each other along the axial direction. The push surface and the contact support portion may maintain a state of surface contact with each other.

[0042] Furthermore, an elastic member that extends and retracts along the axial direction can be provided between the gear assembly and the clutch. The elastic member can provide an elastic force to the clutch in the axial direction. As described above, in this invention, a prior art spring (elastic member) used to move the clutch can also be used to reset the pusher to its initial position. Therefore, there is no need to provide an additional spring in the clutch drive device, thereby reducing the number of parts and assembly work.

[0043] Additionally, the drive cam may include: a first cam portion whose axial length increases or decreases along the circumference of the drive member; and a second cam portion connected to the first cam portion, having an inclination angle relative to the circumference of the drive member that is smaller than the inclination angle of the first cam portion.

[0044] Furthermore, a sensing enclosure can be provided along the circumference of the driving member at its edge. A sensing avoidance portion, omitting the sensing enclosure, can also be formed along the circumference of the driving member at its edge. During rotation of the driving member, the sensing enclosure can interfere with the sensing switch, causing the sensing switch to open or close. During rotation of the driving member, the sensing avoidance portion can cause the sensing switch to close or open. As described above, the present invention provides a sensing structure that utilizes the rotation of the driving member to activate the sensor switch, thereby improving the control reliability of the clutch drive device.

[0045] Additionally, the driving member may be provided with a driving cam extending circumferentially along the driving member. Sensing enclosures may be provided circumferentially along the edge of the driving member. The driving member may be provided with the same number of driving cams.

[0046] Furthermore, at least one of the surfaces of the driving member and the opposing surface of the pusher is provided with a cam portion that interferes with the other in the circumferential direction.

[0047] Invention Effects

[0048] The roller rotation device and the garment processing device including the present invention, as described above, have the following effects.

[0049] In this invention, the drive member and pusher member constituting the clutch drive device can be aligned along the axial direction of the roller rotating device. As described above, if the clutch drive device is aligned along the axial direction of the roller rotating device, it is possible to prevent an increase in the radial dimension of the roller rotating device due to the clutch drive device, and it is possible to miniaturize the roller rotating device and the garment handling device.

[0050] Furthermore, the radial dimension of the drum rotating device does not increase due to the clutch drive device, therefore the clutch drive device of the present invention can also be applied to small-sized drum rotating devices. Thus, the clutch drive device of the present invention not only improves interchangeability but also enables miniaturization of the drum rotating device.

[0051] In particular, the drive component and pusher of the clutch drive unit can be concentrically arranged on the drive shaft and overlap each other radially. This reduces the axial dimension of the clutch drive unit and allows for miniaturization of both the clutch drive unit and the drum rotation device.

[0052] Furthermore, in this invention, the pusher member constituting the clutch drive device can move axially and disengage or engage with the coupler by causing the clutch to move axially. As described above, since the pusher member of the clutch drive device moves axially in the same direction as the clutch, it is not necessary to transmit the rotational force of the drive source (motor) radially to the pusher member. Therefore, the structure for power transmission in the clutch drive device becomes simpler, and more direct power transmission is achieved, thereby improving power transmission efficiency.

[0053] In particular, this invention omits power transmission structures such as levers arranged radially between the clutch and the drive source, as well as additional springs for lever reset, so that the drive member concentrically arranged on the motor shaft can rotate and move the pusher. Therefore, it has the advantage of reducing the load on the drive source (motor) used to drive the clutch drive unit, and of applying a small motor to the clutch drive unit.

[0054] Furthermore, in this invention, the pusher constituting the clutch drive device can move only linearly along the axial direction, and the drive member that actuates the pusher only rotates around the drive shaft, thus achieving duality. In this way, the drive member does not need to move linearly, and therefore the gear shape for linkage with the drive source and the cam shape for moving the pusher can be easily implemented. Therefore, the durability of the drive member and the operational reliability of both the drive member and the pusher can be improved.

[0055] Furthermore, in this invention, the existing spring (elastic member) that moves the clutch can be used to reset the pusher to its initial position. Therefore, there is no need to install an additional spring in the clutch drive unit, thereby reducing the number of parts and assembly work.

[0056] Furthermore, in this invention, the clutch drive unit is axially positioned between the motor and the gear assembly (reducer), allowing the clutch drive unit to engage with both the motor and the gear assembly separately. The motor can be connected to the gear assembly via the clutch drive unit, eliminating the need for additional structures for motor mounting. Therefore, the number of components required for motor mounting is reduced, and the motor is secured during clutch drive unit installation, thus reducing assembly work.

[0057] Furthermore, in this invention, a drive cam is provided circumferentially on the drive member, so the drive member can rotate continuously in one direction and raise and lower the pusher member. Therefore, the drive source that actuates the drive member can also rotate only in one direction, and the operating mechanism of the clutch drive device can be simply realized.

[0058] Furthermore, the drive member and the pusher member constituting the present invention can be provided with corresponding cam structures (drive cam portion and driven cam portion) that are in surface contact with each other, thereby allowing the rotational motion of the drive member to be switched into the linear motion of the pusher member. This provides the advantage of not only improving the operational reliability of the clutch drive device but also reducing the load on the drive source through the tilt angle of the cam structure.

[0059] Furthermore, in this invention, the clutch, drive member, and pusher can overlap each other radially. This allows for a further reduction in the axial length of the clutch drive mechanism, and consequently, a reduction in the axial length of the garment handling device.

[0060] Furthermore, in this invention, the sensor switch can be turned on / off during the rotation of the drive member. If the sensor switch operates in conjunction with the rotation of the drive member, the control unit can sense the rotation angle of the drive member and control the drive member. As described above, this invention enables a mechanism sensing structure that uses the rotation of the drive member to activate the sensor switch, thereby improving the control reliability of the clutch drive device. Attached Figure Description

[0061] Figure 1 This is a perspective view showing the structure of an embodiment of a garment processing apparatus to which the drum rotation device of the present invention is applied.

[0062] Figure 2 This is a perspective view showing the structure of the housing and outer tub of one embodiment of the garment handling apparatus of the present invention.

[0063] Figure 3 This is a perspective view showing the rear structure of a garment processing apparatus to which the drum rotation device of the present invention is applied, according to an embodiment.

[0064] Figure 4 This is a perspective view illustrating an embodiment of the drum rotation device of the present invention.

[0065] Figure 5 yes Figure 4 A cross-sectional view of the V-V' line.

[0066] Figure 6 This is an enlarged cross-sectional view showing the internal structure of an embodiment of the present invention.

[0067] Figure 7 This is a cross-sectional view showing the configuration of the coupling and rotor connection that constitutes an embodiment of the present invention.

[0068] Figure 8 This is a cross-sectional view showing the configuration of a clutch that separates the coupler from the rotor, constituting an embodiment of the present invention.

[0069] Figure 9 This is an exploded perspective view showing a plurality of components constituting an embodiment of the present invention.

[0070] Figure 10 It is to decompose the components constituting an embodiment of the present invention and from the... Figure 9 A three-dimensional image shown from different angles.

[0071] Figure 11 This is a perspective view showing the structure of a bearing housing, motor, coupler, and clutch drive device constituting an embodiment of the present invention.

[0072] Figure 12 This is a perspective view showing the configuration of a motor combined with a clutch drive device, which constitutes an embodiment of the present invention.

[0073] Figure 13 This is an exploded perspective view showing the components constituting a clutch drive device according to an embodiment of the present invention.

[0074] Figure 14 It is a disassembly of the components constituting a clutch drive device according to an embodiment of the present invention and from the... Figure 13 A three-dimensional image shown from different angles.

[0075] Figure 15 This is a perspective view showing the structure of a clutch drive device constituting an embodiment of the present invention.

[0076] Figure 16 It is the removal of the second housing of the clutch drive device constituting an embodiment of the present invention and from the... Figure 15 A three-dimensional image shown from different angles.

[0077] Figure 17 This is a perspective view showing the state of the clutch drive device constituting an embodiment of the present invention with the first housing removed.

[0078] Figure 18 This is a perspective view showing the coupler, drive member, and pusher member that constitute an embodiment of the present invention in a state of separation from each other.

[0079] Figure 19 This is a perspective view showing the state in which the drive member and the pusher member constituting an embodiment of the present invention are separated from each other.

[0080] Figure 20 This is a perspective view showing the structure of a drive member constituting an embodiment of the present invention.

[0081] Figure 21 This is a perspective view showing the structure of a pusher that constitutes an embodiment of the present invention.

[0082] Figure 22This is a top view showing the state of the clutch drive device constituting an embodiment of the present invention with the first housing removed.

[0083] Figures 23 to 25 This is a diagram showing the operational state of a process in which a driving member, constituting an embodiment of the present invention, rotates to raise a pushing member.

[0084] Figures 26 to 29 This is a diagram showing the operational state of a process in which a driving member, constituting an embodiment of the present invention, rotates to raise a pushing member.

[0085] Figure 30 This is a conceptual diagram showing, in an unfolded state, the drive cam of the drive member constituting an embodiment of the present invention, the sensing path, and the driven cam of the pusher.

[0086] Figures 31 to 34 This is a conceptual diagram showing the positional relationship between the driving cam and the driven cam when the driving member constituting an embodiment of the present invention rotates.

[0087] Figure 35 This is a perspective view showing the drive member and pusher member constituting the second embodiment of the drum rotating device of the present invention in a state of separation from each other.

[0088] Figure 36 This is a perspective view showing the drive member and pusher member constituting the third embodiment of the drum rotation device of the present invention in a state of separation from each other.

[0089] Figure 37 This is a perspective view showing the drive member and pusher member constituting the fourth embodiment of the drum rotation device of the present invention in a state of separation from each other. Detailed Implementation

[0090] Hereinafter, some embodiments of the present invention will be described in detail with reference to the exemplary accompanying drawings. It should be noted that when assigning reference numerals to the constituent elements of the various drawings, the same reference numerals are assigned to the same constituent elements as much as possible, even if they are shown in different drawings. Furthermore, in describing the embodiments of the present invention, detailed descriptions of related well-known structures or functions are omitted when it is determined that a detailed explanation would hinder understanding of the embodiments of the present invention.

[0091] This invention relates to a drum rotation device 100 and a garment handling apparatus including the same. Here, a garment handling apparatus refers to a household appliance, such as a washing machine or dryer, in which an internal drum 30 rotates. The garment handling apparatus may also include household appliances that simultaneously perform washing and drying functions. The following description uses a washing machine as an example of a garment handling apparatus.

[0092] Figure 1A washing machine is shown as a clothes handling device using the drum rotation device 100 of this embodiment. As shown, the frame of the washing machine can be formed by a shell 10 that is approximately hexahedral in shape. The shell 10 may include a frame 11 that constitutes the exterior. A door 15 may be disposed at the front of the shell 10. When the door 15 is opened, the storage space S1 inside the washing machine can be exposed. The user can put laundry into the storage space S1.

[0093] For reference, "front" refers to the front of the housing 10 where the door is located, and "rear" refers to the rear of the housing 10, which is opposite to "front". Figure 1 Based on this, users can put the laundry in from the back and take it out from the front. In the diagram, reference numeral F indicates the front, and reference numeral R indicates the back.

[0094] Additionally, the term "axial" below refers to the length direction of the output shaft 80, as described later. The "axial" direction can also be the length direction of the motor shaft 340. The term "radial" below refers to a direction orthogonal to the axial direction, for example, a direction extending radially from the center of the rotor 230 constituting the motor 200.

[0095] The storage space S1 can be formed inside the roller 30. The roller 30, as a rotating body, can have a shape that surrounds the storage space S1. The roller 30 can be combined with a spider frame 53. The spider frame 53 is combined with the roller 30. Therefore, if the spider frame 53 rotates via the roller rotating device 100, the roller 30 can also rotate together.

[0096] exist Figure 2 The structure of the frame 11 forming the skeleton of the housing 10 and the outer barrel 50 is shown. For reference, the roller rotating device 100 is disposed between the rear of the outer barrel 50 and the housing 10, thus in Figure 2 The outer barrel 50 is not visible. It can surround the roller 30. That is, the outer barrel 50 is an outer groove, while the roller 30 is an inner groove. Reference numeral S2 is the rotational space surrounded by the outer barrel 50, in which the roller 30 can be arranged. The outer barrel 50 is attached to the housing 10 and does not rotate, while the roller 30 can rotate relative to the outer barrel 50.

[0097] A rotating disc (not shown) may be provided inside the outer tub 50. The rotating disc can perform a washing function by creating a water flow, and can wash the laundry in the drum 30 while rotating. The rotating disc can also be called a pulsator.

[0098] Figure 3 The rear structure of the outer barrel 50 is shown. For reference, in Figure 3 The housing 10 that covers the back of the outer tub 50 is omitted, leaving the rear of the outer tub 50 exposed. A motor 200 of a roller rotating device 100 can be disposed at the center of the rear of the outer tub 50. The motor 200 can receive an external power source to generate rotational force. Figure 3 The rotor 230 constituting the motor 200 is shown, but the stator 220 and gear assembly 300, which will be described later, are arranged inside the rotor 230.

[0099] The outer barrel 50 may include a generally cylindrical outer barrel body 51. The front of the outer barrel body 51 is open, serving as the entrance to the rotation space S2. The motor 200 may be disposed on the back of the outer barrel body 51. A metal reinforcing member (not shown) may be built into the outer barrel body 51 to improve its strength.

[0100] A back wall 55 may be provided on the back side of the outer barrel body 51. The back wall 55 protrudes rearward from the back side of the outer barrel 50. The back wall 55 may be generally annular in shape. The back wall 55 may surround the motor 200 and the gear assembly 300. A plurality of reinforcing ribs may be arranged around the periphery of the back wall 55.

[0101] Reference Figure 4 A drive unit cover 60 may be disposed inside the outer barrel body 51. The drive unit cover 60 may house the bearings B1-B6 and the gear assembly 300, which will be described later. The drive unit cover 60 may include a first cover 61 and a second cover 63 coupled to the first cover 61. (Refer to...) Figure 5 As can be seen, a defined space, more precisely, a drive space 62, is formed between the first cover 61 and the second cover 63. The gear assembly 300 and the two cover bearings B3 and B4 (described later) can be configured in the drive space 62. The drive cover 60 can also be considered part of the gear assembly 300.

[0102] Reference Figure 5 The output shaft 80 and the motor shaft 340 can be configured to be coaxial with each other. Specifically, the output shaft 80 and the motor shaft 340 can be configured to be axially aligned with each other. A gear assembly 300 can be disposed between the output shaft 80 and the motor shaft 340 to transmit the rotational force of the motor shaft 340 to the output shaft 80. More precisely, when performing a washing mode using the garment handling device, the gear assembly 300 can reduce the rotation of the motor shaft 340 and transmit it to the output shaft 80.

[0103] For reference, in the washing mode and the initial spin-drying mode after washing, the weight inside the drum 30 is the sum of the weight of the laundry and the weight of the water used for washing. Therefore, it is necessary for the drum rotation device 100 to operate with a relatively large torque and a slow speed. Conversely, in the spin-drying mode, the weight of the water inside the drum 30 is relatively small. Therefore, it is necessary for the drum rotation device 100 to operate with a relatively small torque and a high speed. Hereinafter, the distinction between "washing mode" and "spin-drying mode" will be explained.

[0104] In this embodiment, the output shaft 80 may include two output shafts 80 coaxially arranged with each other. The two output shafts 80 include a first output shaft 81 and a second output shaft 85 surrounding the first output shaft 81. In this embodiment, the first output shaft 81 is coupled to the drum 30 for dehydration, allowing the drum 30 to rotate. The second output shaft 85 is coupled to a rotating disc 40 for washing, thereby allowing the rotating disc to rotate.

[0105] The first output shaft 81 and the second output shaft 85 can rotate differently depending on the driving mode of the garment handling device. For example, when the garment handling device is in spin-drying mode, the first output shaft 81 can be directly connected to the rotor 230 and rotate at high speed. On the other hand, when the garment handling device is in washing mode, the second output shaft 85 can be rotated at a reduced speed by the gear assembly 300. Therefore, the first output shaft 81 can be referred to as the spin-drying shaft, and the second output shaft 85 can be referred to as the washing shaft.

[0106] At this time, the first output shaft 81 can be selectively connected to the rotor 230. If the rotor 230 is connected to the first output shaft 81, a dehydration mode is executed; if the rotor 230 is disconnected from the first output shaft 81, the dehydration mode is stopped. As described above, a clutch 410 is provided for selectively connecting the first output shaft 81 to the rotor 230. The clutch 410 moves along the axial direction, thereby engaging / disengaging with the coupler 350 provided on the rotor 230. In this invention, the clutch drive device 400 can move the clutch 410 axially, thereby determining whether the first output shaft 81 rotates. This mode of operation is described in detail below.

[0107] Reference Figure 5This describes the power transmission process in the washing and spin-drying modes. First, if the washing mode is selected, the clutch 410 is in the disengaged state. Here, "disengaged state" means that the clutch 410 is separated from the coupling 350 of the rotor 230, and the rotational force of the rotor 230 is not transmitted to the clutch 410. More precisely, the disengaged state is the state in which the clutch 410 is disengaged from the clutch engagement portion 351 of the coupling 350. This disengaged state of the clutch 410 can be achieved by the clutch drive device 400. If the clutch drive device 400 overcomes the elastic force of the elastic member S (described later) and moves the clutch 410 forward (in the F direction) away from the coupling 350, the clutch 410 can be switched to the disengaged state. The detailed drive of the clutch drive device 400 will be explained again below.

[0108] For reference only. Figure 6 The dashed line in the middle indicates the state in which the clutch 410 is disengaged. Figure 6 The clutch 410, represented by a solid line, indicates the engaged state, in which the clutch 410 is engaged with the coupler 350. Hereinafter, "engaged state" refers to the state in which the clutch 410 is engaged with the coupler 350.

[0109] Refer again Figure 5 If the clutch 410 is disengaged, when the rotor 230 rotates, the rotational force of the rotor 230 is transmitted to the motor shaft 340 coupled to the rotor 230, thereby causing the motor shaft 340 to rotate (in the direction of arrow ①). If the motor shaft 340 rotates, the rotational force of the motor shaft 340 is transmitted to the gear assembly 300. More precisely, if the motor shaft 340 rotates, the sun gear 343 disposed on the motor shaft 340 rotates. The rotational force of the sun gear 343 is transmitted to the plurality of pinions 370 meshing with the sun gear 343 (in the direction of arrow ②).

[0110] The plurality of pinions 370 move along a fixed internal gear section 330. Here, the movement of the plurality of pinions 370 along the internal gear section 330 constitutes revolution. Simultaneously, the plurality of pinions 370 rotate in the opposite direction to the sun gear 343. That is, the plurality of pinions 370 rotate simultaneously while revolving around the sun gear.

[0111] Furthermore, the rotational force generated by the revolution of the plurality of pinions 370 is transmitted to the planet carrier 361 constituting the gear assembly 300 (arrow ③ direction). The rotational force of the planet carrier 361 is transmitted to the second output shaft 85 coupled to the planet carrier 361 (arrow ④ direction). The second output shaft 85 rotates together with the planet carrier due to the transmitted rotational force, thereby causing the rotating disk to rotate. Arrow ⑤ indicates the direction of rotation of the second output shaft 85.

[0112] As described above, in the disengaged state where the clutch 410 is separated from the coupler 350, the plurality of pinions 370 simultaneously revolve and rotate, during which a decrease in rotational speed and a resulting increase in torque occur. Therefore, the above-mentioned operation can be achieved when the rotation of the drum 30 requires a large force or the rotation of the rotating disc, for example, in a washing mode where the weight of water increases or in the initial spin-drying mode at the start of spin-drying.

[0113] On the other hand, utilizing Figure 5 The power transmission process in the dehydration mode is described. In the dehydration mode, the clutch 410 is in an engaged state, connected to the coupler 350. The clutch 410 can switch from a previously disengaged state to an engaged state by the clutch drive device 400. More precisely, the clutch 410 can be in an engaged state due to the clutch drive device 400 and the elastic member S. If the clutch drive device 400 is driven, the elastic member S can move the clutch 410 toward the coupler 350, thereby engaging the clutch 410 with the coupler 350. As described above, in this embodiment, there is no need to provide an additional spring for the operation of the clutch drive device 400; the pusher 460 can be moved using the elastic member S for moving the clutch 410, thus reducing the number of parts and assembly work.

[0114] If the clutch 410 is engaged with the coupler 350, then the clutch 410 also rotates with the rotor 230 because the coupler 350 rotates together with the rotor 230. That is, the clutch 410 is directly connected to the rotor 230 through the coupler 350, and thus can rotate at the same speed as the rotor 230. Figure 6 The clutch 410, indicated by a solid line, represents the state of engagement with the coupler 350. Here, the clutch 410 is engaged with the clutch engagement portion 351 that constitutes the coupler 350.

[0115] More specifically, in the engaged state, the rotational force of the rotor 230 is transmitted to the clutch 410 (in the direction of arrow ①') via the coupler 350. The rotational force of the clutch 410 is then transmitted to the gear housings 310 and 320 that constitute the gear assembly 300. Consequently, the gear housings 310 and 320 rotate together with the clutch 410.

[0116] More accurately, refer to Figure 6 The first gear cover 310, constituting the gear covers 310 and 320, may be provided with a cover gear portion 325. The cover gear portion 325 may be configured to surround the motor shaft 340 and can engage with the clutch 410 to rotate together. The first gear cover 310 and the second gear cover 320 are engaged with each other, so that the second gear cover 320 and the first gear cover 310 can rotate together. That is, the rotational force of the clutch 410 is transmitted to the first gear cover 310 (arrow ②' direction), and the rotational force of the first gear cover 310 is transmitted to the second gear cover 320 (arrow ③' direction).

[0117] The second gear housing 320 engages with the first output shaft 81, thereby transmitting the rotational force of the second gear housing 320 to the first output shaft 81 (in the direction of arrow ④'). Consequently, the first output shaft 81 rotates together with the gear housings 310 and 320. Arrow ⑤' indicates the direction of rotation of the first output shaft 81.

[0118] At this time, the internal gear section 330 disposed inside the gear housings 310 and 320 also rotates together with the gear housings 310 and 320. When the internal gear section 330 rotates (revolves), it causes the plurality of pinions 370 meshing with it to revolve at the same speed. The motor shaft 340 also rotates together with the rotor 230, but because the internal gear section 330 revolves itself, the sun gear 343 does not rotate along the internal gear section 330. Therefore, the rotational speed of the motor shaft 340 is the same as the rotational speed of the gear housings 310 and 320, and also the same as the rotational speed of the second output shaft 85.

[0119] That is, when the clutch 410 is engaged, the first output shaft 81 and the second output shaft 85 rotate at the same high speed, and the roller 30 engaged with the first output shaft 81 and the rotating disk 40 engaged with the second output shaft 85 also rotate at the same speed. As a result, the rotating disk 40 and the roller 30 can rotate at the same speed as the rotor 230, and the roller 30 can rotate at a high speed. The clutch 410 is engaged when high-speed rotation of the roller 30 is required but not with excessive force, for example, during the dehydration mode.

[0120] Figure 7 and Figure 8 The diagrams show the clutch 410 in both engaged and disengaged states. The clutch 410 can switch between these states. The clutch drive device 400 can move the clutch 410 along the axial direction, thereby switching from the engaged state to the disengaged state, and vice versa.

[0121] Figure 7 In this configuration, the clutch 410 moves rearward and engages with the coupler gear 352. The clutch gear 417 of the clutch 410 is in a state where it can engage with the coupler gear 352 and rotate together. Therefore, the clutch 410 rotates together with the coupler gear 352, resulting in a rotation speed similar to that of the rotor 230. (Refer to...) Figure 10 The coupler gear 352 is disposed at the clutch engagement portion 351 of the coupler 350. Figure 7 The direction of arrow ① indicates the direction in which the clutch 410 moves towards the engaged state, which is the same direction in which the elastic member S provides elastic force to the clutch 410. The direction of arrow ② indicates the direction in which the clutch drive device 400 switches the clutch 410 to the disengaged state.

[0122] Reference Figure 8 The clutch 410 moves forward, thus disengaging. If the clutch 410 moves forward, the clutch gear 417 of the clutch 410 disengages axially from the coupler gear 352, thereby releasing them from their meshing state. Therefore, rotation of the coupler gear 352 will not cause rotation of the clutch 410.

[0123] As described above, the clutch drive device 400 can move the clutch 410 in the longitudinal direction, i.e., the axial direction, thereby changing the power transmission process of the rotor 230. The following description focuses on the power transmission structure of this clutch drive device 400.

[0124] Reference Figure 5 and Figure 10 The drive unit cover 60 will be described below. The drive unit cover 60 is disposed on the opposite side of the motor 200, separated from the clutch drive device 400. The drive unit cover 60 can be mounted on the outer barrel 50. The drive unit cover 60 remains fixed and does not rotate. A drive space 62 is formed inside the drive unit cover 60. The gear assembly 300 and the two cover bearings B3 and B4 can be disposed in the drive space 62.

[0125] The drive unit cover 60 can be formed by a cover body 61 and a cover cover 63 to form a skeleton. If the cover body 61 and the cover cover 63 are combined with each other, the drive space 62 can be formed therebetween. In this embodiment, the cover body 61 is disposed rearward than the cover cover 63.

[0126] A portion of the output shaft 80 may be configured within the drive space 62. (See reference...) Figure 5 A portion of the first output shaft 81 and a portion of the second output shaft 85 are respectively disposed inside the drive space 62, with another portion protruding forward from the drive space 62. A portion of the output shaft 80 can engage with the gear assembly 300 inside the drive space 62.

[0127] Next, the motor 200 will be described. 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 of laminated metal sheets and an insulator 221 surrounding the core 223. The insulator 221 prevents current flowing in the coils 222 wound around the teeth of the core 223 from being directly transmitted to the core 223 side.

[0128] The rotor 230 can be configured to surround the stator 220. The rotor body 231, which forms the frame of the rotor 230, has a diameter larger than that of the stator 220. A rotor center opening 232 can be opened at the center of the rotor body 231. A motor shaft 340 can be disposed in the rotor center opening 232.

[0129] The rotor 230 can be configured such that the permanent magnet 233 faces the core 223. If power is applied to the core 223 through the connector portion 250, the rotor 230 can rotate due to the induced electromotive force. Alternatively, the rotor 230 may contain the core 223 and a coil, and the stator 220 may contain the permanent magnet 233. Reference numeral 235 indicates a mating hole into which the fixing protrusion 354 of the clutch engagement portion 351 constituting the coupler 350 is inserted.

[0130] A gear assembly 300 is connected to the motor 200. The gear assembly 300 may include gear housings 310 and 320, an internal gear section 330, a motor shaft 340, a coupler 350, a planetary carrier 360, and a plurality of pinions 370. They can rotate in conjunction with each other. The linkage structure of the gear assembly 300 is described in detail below.

[0131] The gear housings 310 and 320 and the internal gear portion 330 can form a ring gear and rotate integrally with each other. That is, the ring gear may include the gear housings 310 and 320 and the internal gear portion 330. The internal gear portion 330 is disposed inside the gear housings 310 and 320. The gear housings 310 and 320 and the internal gear portion 330 are coupled to each other, so that they can rotate or stop together. As another example, the gear housings 310 and 320 and the internal gear portion 330 can be integrally formed.

[0132] The gear housings 310 and 320 may include a first gear housing 310 and a second gear housing 320. The first gear housing 310 and the second gear housing 320 can be coupled together, thereby forming an internal space. More precisely, if the first gear housing 310 and the second gear housing 320 are coupled together, an internal space is formed on their inner sides. In this internal space, the sun gear 343 and the plurality of pinions 370 can be linked together. As another example, the gear housings 310 and 320 may consist of only the first gear housing 310 or the second gear housing 320.

[0133] If the first gear cover 310 and the second gear cover 320 are joined together, the gear covers 310 and 320 can be formed into a generally cylindrical shape. The central portion of the gear covers 310 and 320 can extend through the center axially. In this embodiment, the motor shaft 340 passes through the central portion of the first gear cover 310, and the output shaft 80 passes through the central portion of the second gear cover 320.

[0134] Reference Figure 9 and Figure 10 The gear assembly 300 is described in detail below. The first gear cover 310 may have an inner recessed cylindrical shape. A first cover hole 311 is formed through the center of the first gear cover 310, through which the output shaft 80 can pass.

[0135] A second gear cover 320 is attached to the opposite side of the first gear cover 310. The second gear cover 320 may have a generally circular plate shape. The second gear cover 320 is configured to be closer to the rotor 230 than the first gear cover 310. A cover gear portion 325 may be provided in the second gear cover 320. The cover gear portion 325 is used to engage with the clutch 410. Through the cover gear portion 325, the second gear cover 320 can engage with the clutch 410 and rotate together.

[0136] The gear housing portion 325 can protrude axially from the center of the second gear housing 320. The gear housing portion 325 protrudes in a generally cylindrical shape, and the motor shaft 340 can be disposed therein, thereby surrounding the motor shaft 340. (Refer to...) Figure 6 One end of the gear portion 325 of the housing is configured to face each other axially with the motor shaft coupling portion 355 of the coupler 350.

[0137] A cover gear tooth 326 may be provided on the surface of the cover gear portion 325. The cover gear tooth 326 has a gear shape provided on the surface of the cover gear portion 325, and can engage with the inner circumferential surface gear tooth 415 formed on the inner circumferential surface of the clutch 410 (see reference). Figure 7 The gear teeth 326 and 415 engage, allowing the clutch 410 to transmit the rotational force of the rotor 230 to the gear housings 310 and 320. In this embodiment, because the inner circumferential gear teeth 415 and 326 engage, the clutch 410 and the gear housings 310 and 320 always rotate or stop together.

[0138] Reference Figure 9 An internal gear portion 330 may be disposed inside the gear housings 310 and 320. The internal gear portion 330 may be formed in a ring shape. The internal gear portion 330 is coupled to the gear housings 310 and 320, thereby allowing it to rotate integrally with the gear housings 310 and 320. For this coupling, the internal gear portion 330 may be provided with an inner protrusion 332 that engages with the gear housings 310 and 320. The inner protrusion 332 may protrude axially from the surface of the internal gear portion 330.

[0139] Internal gear teeth 335 are provided on the inner surface of the internal gear section 330. The internal gear teeth 335 mesh and rotate with a plurality of pinions 370. The plurality of pinions 370 rotate in a state where the plurality of pinions 370 and the internal gear teeth 335 are meshed with each other, and the plurality of pinions 370 (i) mesh and rotate (revolve and rotate) with the internal gear section 330 that is not receiving rotational force (washing mode) or (ii) mesh and rotate (revolve) with the internal gear section 330 in a rotating (revolve) state (spinning mode). The internal gear teeth 335 and the plurality of pinions 370 may be helical gears. As another example, the internal gear teeth 335 and the plurality of pinions 370 may also be spur gears.

[0140] The gear assembly 300 includes a motor shaft 340. The motor shaft 340 receives the rotational force of the rotor 230, and therefore can also be considered an input shaft. The motor shaft 340 rotates integrally with the rotor 230. The motor shaft 340 always rotates with the rotor 230 as the rotor 230 rotates, thereby transmitting the rotational force to the output shaft 80 through the gear assembly 300.

[0141] A rotor connecting portion 341 and a sun gear 343, spaced apart axially from each other, may be provided on the outer peripheral surface of the motor shaft 340. The rotor connecting portion 341 may be located on the outer peripheral surface of the motor shaft 340 and connected to the rotor 230. The rotor connecting portion 341 may be a spline or a serration. The rotor connecting portion 341 may be engaged at the center of the motor shaft engagement portion 355, which will be described later. The rotor connecting portion 341 is not a gear structure, but rather a structure that engages with the motor shaft engagement portion 355, thereby causing the motor shaft 340 to rotate together with the coupler 350.

[0142] The sun gear 343 can be spaced apart from the rotor connection portion 341 along the axial direction of the motor shaft 340. The sun gear 343 can mesh with a plurality of pinions 370. The sun gear 343 connects the rotation of the motor shaft 340 to the rotation of the plurality of pinions 370. The sun gear 343 can be formed with a diameter larger than that of the rotor connection portion 341. The sun gear 343 can be composed of helical gears or spur gears, etc.

[0143] A planetary carrier 360 is disposed on the gear housings 310 and 320. The planetary carrier 360 can support the rotation of a plurality of pinions 370 and rotate around the plurality of pinions 370. More precisely, the planetary carrier 360 can rotate in conjunction with the orbital motion of the plurality of pinions 370. (See reference...) Figure 10An output section 362 is provided on the planetary carrier 360, which causes the second output shaft 85 to rotate. That is, it can be seen that the result of the rotational action of the gear assembly 300 is transmitted to the second output shaft 85 through the planetary carrier 360.

[0144] From the structure of the planetary carrier 360, the planetary carrier 360 includes a planetary carrier body 361 and a planetary carrier cover 365. The planetary carrier body 361 is configured to be spaced further forward than the planetary carrier cover 365, separated by a plurality of the pinions 370. An output portion 362 protrudes from the planetary carrier body 361. The output portion 362 is formed with splines or serrations, allowing it to engage with the outer peripheral surface of the second output shaft 85. Splines or serrations may also be formed on the outer peripheral surface of the second output shaft 85.

[0145] The planetary carrier body 361 may be provided with a plurality of pinion shafts 363, and shaft support holes 367 may be formed in the planetary carrier cover 365 at positions corresponding to the plurality of pinion shafts 363. One end of the plurality of pinion shafts 363, which serve as the rotation shafts of the plurality of pinions 370, can be inserted into the shaft support holes 367. In this embodiment, the gear assembly 300 has a total of four pinions 370, therefore the plurality of pinion shafts 363 and shaft support holes 367 may also be composed of four pairs. The plurality of pinion shafts 363 may also be composed of components separate from the planetary carrier body 361.

[0146] Referring to the plurality of pinions 370, the plurality of pinions 370 are configured to surround the sun gear 343. The plurality of pinions 370 mesh and rotate with the sun gear 343 and the internal gear portion 330. More precisely, it can be considered that the plurality of pinions 370 are disposed between the outer circumferential surface of the sun gear 343 and the inner circumferential surface of the internal gear portion 330, thereby outputting the rotational force input through the sun gear 343 to the internal gear portion 330. If the clutch 410 is in the disengaged state, the internal gear portion 330 does not rotate or rotates at a very slow speed. Therefore, in the disengaged state, the plurality of pinions 370 can rotate on their own axes while revolving around the internal gear portion 330. Conversely, if the clutch 410 is engaged, the internal gear 330 rotates together with the clutch 410. Therefore, the plurality of pinions 370 do not rotate on their own axis, but instead revolve around the sun gear 343 while rotating together with the internal gear 330.

[0147] Reference Figure 5 and Figure 9The description includes bearings B1-B6 that assist in the rotation of the gear assembly 300. Bearings B1-B6 may include a first support bearing B1 and a second support bearing B2. The first support bearing B1 and the second support bearing B2 are axially spaced apart from each other, thereby supporting the rotation of the motor shaft 340 respectively. Alternatively, one of the first support bearing B1 and the second support bearing B2 may be omitted, or the first support bearing B1 and the second support bearing B2 may be arranged radially.

[0148] Cover bearings B3 and B4 may be disposed between the drive housing 60 and the gear housings 310 and 320. The cover bearings B3 and B4 support the rotation of the gear housings 310 and 320 relative to the drive housing 60. In this embodiment, the cover bearings B3 and B4 consist of a pair of cover bearings B3 and B4 spaced apart from each other along the axial direction.

[0149] Shaft bearings B5 and B6 may be disposed between the first output shaft 81 and the second output shaft 85. The shaft bearings B5 and B6 facilitate smooth relative rotation between the first output shaft 81 and the second output shaft 85. In this embodiment, the two shaft bearings B5 and B6 are configured to be axially spaced apart from each other.

[0150] Next, the clutch 410 and the clutch drive device 400 that drives the clutch 410 will be described. The clutch drive device 400 uses rotation input through the drive source 441 to move the clutch 410. At this time, the clutch 410 can also be regarded as part of the clutch drive device 400.

[0151] For ease of explanation, the clutch 410 will first be described, which may have a generally tube shape. Figure 18 In the accompanying drawings, reference numeral 412 denotes the clutch body 412 that forms the skeleton of the clutch 410. With the clutch body 412 positioned at the center of the clutch drive device 400, the clutch 410 can move along the axial direction. An axially penetrating clutch hole 411 is formed at the center of the clutch body 412. The motor shaft 340 and the housing gear portion 325 can pass through the clutch hole 411.

[0152] A contact support portion 413 may be provided at the edge of the clutch hole 411. The contact support portion 413 is provided in the direction in which the diameter of the clutch 410 increases. The contact support portion 413 is the portion pushed by the pusher 460. More precisely, the pusher surface 462a of the pusher 460 (refer to...) Figure 23The contact support 413 can be lifted axially. The contact support 413 can act as a stopper that is stopped by the pushing surface 462a of the pusher 460 to limit the range of movement of the clutch 410.

[0153] Inner peripheral gear teeth 415 may be provided on the inner peripheral surface of the clutch hole 411. The inner peripheral gear teeth 415 mesh with the gear teeth 326 of the gear housing, so that the clutch 410 can transmit the rotational force of the rotor 230 to the gear housings 310 and 320. In this embodiment, the inner peripheral gear teeth 415 and the gear teeth 326 mesh, so that the clutch 410 and the gear housings 310 and 320 always rotate or stop together.

[0154] A clutch gear 417 may be provided on the clutch body 412. The clutch gear 417 may be located on the opposite side of the contact support portion 413. When the clutch 410 moves rearward, the clutch gear 417 engages with the coupler gear 352 of the coupler 350. If the clutch gear 417 engages with the coupler gear 352, the clutch 410 rotates together with the rotor 230. As a result, the gear covers 310 and 320 and the internal gear portion 330 connected to the clutch 410 can also rotate together.

[0155] The clutch gear 417 may have a gear structure. (Refer to...) Figure 18 The clutch gear 417 includes the protrusion and recess of the clutch 410. The protrusion and recess of the clutch 410 has a continuous structure of a rearwardly protruding protrusion 417a and a forwardly recessed groove 417b. This clutch gear 417 engages or disengages with the coupler gear 352 during the axial movement of the clutch 410.

[0156] Reference Figure 11 The clutch drive device 400 can be disposed between the motor 200 and the drive housing 60. The drive housing 60 can also be considered as part of the gear assembly 300, which forms the appearance of the gear assembly 300; therefore, the clutch drive device 400 is disposed between the motor 200 and the gear assembly 300 with axial reference. In this case, both ends of the clutch drive device 400 can engage with the motor 200 and the drive housing 60, respectively. Figure 11Based on this, the motor 200 is coupled to the clutch drive unit 400 from the rear, and the drive unit cover 60 is coupled to the clutch drive unit 400 from the front. In this way, the motor 200 can use the clutch drive unit 400 as a medium to engage with the drive unit cover 60 (gear assembly 300), eliminating the need for additional structures for mounting the motor 200. Therefore, the number of parts for mounting the motor 200 can be reduced, and since the motor 200 is fixed together with the clutch drive unit 400 during installation, the number of assembly workers can also be reduced.

[0157] More precisely, a motor fastening part 240 may be provided on the stator 220 of the motor 200. A cover fastening part 64 may be provided on the drive unit cover 60. A mounting bracket 429 may be provided on the clutch drive device 400, corresponding to the motor fastening part 240 and the cover fastening part 64 respectively. With the cover fastening part 64, the mounting bracket 429 and the motor fastening part 240 aligned, they can be assembled together using fasteners such as bolts (not shown). In this way, the fasteners can simultaneously assemble the drive unit cover 60, the motor 200 and the clutch 410 as three components.

[0158] Figure 11 The diagram shows the clutch 410 configured closer to the front than the clutch drive unit 400, i.e., the drive unit cover 60. However, in practice, if the clutch 410 is assembled rearward between the clutch drive unit 400 and the drive unit cover 60 (to the left of the reference figure), the clutch gear 417 of the clutch 410 can protrude through the center of the clutch drive unit 400 toward the motor 200.

[0159] The elastic member S (refer to) Figure 7 The clutch 410 is pressed backward (towards the motor 200), while the clutch drive unit 400 pushes the clutch 410 forward (towards the drive unit cover 60), thereby switching the clutch 410 from the engaged state to the disengaged state. As described later, if the pusher 460 of the clutch drive unit 400 pushes the contact support 413 of the clutch 410 forward, the clutch 410 is disengaged, moving away from the coupler 350 of the rotor 230. Figure 11 The middle arrow indicates the direction in which the clutch 410 engages with the coupler 350 of the rotor 230.

[0160] Figure 12This illustrates the configuration of the clutch drive device 400 in conjunction with the motor 200. It is evident that the diameter of the clutch drive device 400 is smaller than the diameter of the motor 200. Consequently, the entire clutch drive device 400 does not protrude radially outward from the motor 200. Therefore, it is unnecessary to ensure sufficient area for mounting the clutch drive device 400 in a region offset from the motor 200, allowing for a reduction in the overall size of the roller rotating device 100.

[0161] Reference Figure 13 and Figure 14 The clutch drive device 400 will be described below. The clutch drive device 400 may include a drive housing C. The drive housing C forms the frame of the clutch drive device 400. An actuation space OS1 (see reference) may be formed inside the drive housing C. Figure 6 The motion space OS1 may be equipped with a drive member 450 and a pusher 460. As previously described, the motor 200 and the drive housing 60 can be coupled to each other via the drive housing C.

[0162] In this embodiment, the drive housing C includes a first housing 420 and a second housing 430. The first housing 420 and the second housing 430 are axially coupled to each other. If the first housing 420 and the second housing 430 are coupled to each other, the motion space OS1 (see reference) is formed therebetween. Figure 6 The first housing 420 is configured to be closer to the opposite front, i.e., the gear assembly 300, than the second housing 430. The first housing 420 and the second housing 430 may be joined together by a hook structure (not indicated in the drawings). Alternatively, the first housing 420 and the second housing 430 may also be fastened together by fasteners.

[0163] The first housing 420 and the second housing 430 may each have a generally annular shape or a tube shape. If the first housing 420 and the second housing 430 are assembled together, an axially penetrating hole is formed at the center of the drive housing C. This hole becomes a continuous through-hole 421, 431, connecting the first through-hole 421 formed in the first housing 420 and the second through-hole 431 formed in the second housing 430. As described later, the drive member 450 and the pusher member 460 disposed in the drive housing C also have an annular shape or a tube shape penetrating the center, thus a circular through-hole can be formed at the center of the clutch drive device 400. The motor shaft 340 can pass through these through-holes 421, 431.

[0164] A first through hole 421 formed in the first housing 420 allows the pusher 460 to enter and exit. A portion of the pusher 460 can enter and exit axially through the first through hole 421. Therefore, the first through hole 421 can also be referred to as the pusher moving hole 421. In this case, the radius of the pusher moving hole 421 can be smaller than the radial distance between the center of the pusher 460 and the end of the anti-rotation protrusion 469a (described later). In this way, the anti-rotation protrusion 469a can be engaged with the edge of the pusher moving hole 421, thereby restricting the movement of the pusher 460.

[0165] From the structure of the first housing 420, the framework of the first housing 420 is formed by housing body portions 422 and 425 that are generally annular or short tubular in shape. The housing body portions 422 and 425 can surround the first through hole 421 formed in the center. (Refer to...) Figure 14 The inner side of the first housing 420 may include two ring-shaped housing body portions 422 and 425 with different diameters. The two housing body portions 422 and 425 include an outer body portion 422 and an inner body portion 425. A sensing enclosure 459 of the drive member 450 (described later) may be disposed between the two housing body portions 422 and 425. With the sensing enclosure 459 disposed between the two housing body portions 422 and 425, the drive member 450 can rotate.

[0166] Anti-rotation portions 425a can be formed in the main body portions 422 and 425 of the first housing 420. More precisely, the anti-rotation portion 425a can be formed on the inner circumferential surface of the inner main body portion 425, which is located on the inner side. The anti-rotation portion 425a can prevent the pusher 460 from rotating. The anti-rotation portion 425a can guide the pusher 460 to move only in a straight line along the axial direction without rotation. For this purpose, the anti-rotation portion 425a can be continuously formed along the moving direction of the pusher 460. Figure 13 and Figure 14 Based on this, the anti-rotation part 425a is continuous in the vertical direction.

[0167] The anti-rotation portion 425a has a structure recessed from the inner peripheral surface 425 of the first housing 420. The anti-rotation portion 425a, recessed in this manner, allows the anti-rotation protrusion 469a of the pusher 460 to be inserted. With the anti-rotation protrusion 469a inserted into the anti-rotation portion 425a, the pusher 460 can move axially. The anti-rotation protrusion 469a interferes with the anti-rotation portion 425a, therefore the pusher 460 cannot rotate during axial movement. Alternatively, the anti-rotation portion 425a can protrude from the inner peripheral surface 425 of the first housing 420, and the pusher 460 may also have an anti-rotation groove (not shown) for the insertion of the anti-rotation portion 425a.

[0168] A first drive source mounting portion 428 may be provided in the first housing 420. The first drive source mounting portion 428 is used to house the drive module 440. The drive module 440 may be disposed between the first drive source mounting portion 428 and the second drive source mounting portion 438 (described later), so that the drive module 440 can be shielded by the first housing 420 and the second housing 430. The first drive source mounting portion 428 may have a structure that expands radially from the first housing 420. In this embodiment, the first drive source mounting portion 428 is formed to be axially higher than the center portion of the first housing 420.

[0169] A mounting bracket 429 may be provided in the first housing 420. The mounting bracket 429 protrudes radially from the first housing 420. The mounting bracket 429 can be respectively coupled to the motor 200 and the drive unit cover 60. (Refer to...) Figure 11 With the cover fastening part 64, the mounting bracket 429, and the motor fastening part 240 aligned, they can be assembled together using fasteners such as bolts (not shown). A plurality of mounting brackets 429 can be configured to surround the outer peripheral surface of the first housing 420; in this embodiment, three mounting brackets 429 are disposed on the first housing 420.

[0170] The first housing 420 is coupled to the second housing 430. The second housing 430 may have a structure corresponding to the first housing 420. The second housing 430 and the first housing 420 are coupled to form a drive housing C. The second housing 430 may include a second main body portion 432 in the shape of a ring or a short tube. A fastening platform (not indicated in the drawings) for coupling with the first housing 420 may be provided in the second main body portion 432.

[0171] The second housing 430 may be provided with a drive guide 435, which has a diameter smaller than the second main body portion 432 and surrounds the second through hole 431. The drive guide 435 may have a generally annular shape or a short tube shape. The drive member 450 can rotate in a state surrounding the drive guide 435. The drive member 450 can rotate the drive guide 435 as a rotation axis. More precisely, the guide wall 453 of the drive member 450 can rotate in a state surrounding the drive guide 435.

[0172] A placement space 434, which serves as an empty space, can be formed between the drive guide 435 and the second main body 432. The drive member 450 can be placed in the placement space 434. The placement space 434 is continuously formed along the circumference of the second main body 432, and the drive member 450 rotates in the placement space 434.

[0173] A second drive source mounting portion 438 may be provided in the second housing 430. The second drive source mounting portion 438, together with the first drive source mounting portion 428, can fix the drive module 440. A plurality of components constituting the drive module 440 are arranged between the second drive source mounting portion 438 and the first drive source mounting portion 428. Reference numeral 436 indicates a mounting rib for fixing the drive source 441, on which the drive source 441 may be disposed. A connector mounting portion 437 may be provided adjacent to the second drive source mounting portion 438, on which a drive connector 445 may be disposed.

[0174] A mounting boss 439 may be provided in the second housing 430. The mounting boss 439 protrudes radially outward from the second housing 430 along the axial direction. The mounting boss 439 is housed inside the mounting bracket 429. The mounting boss 439, when housed in the mounting bracket 429, can form a path for fasteners to pass through. For this purpose, the interior of the mounting boss 439 extends through the axial direction.

[0175] A drive module 440 may be configured in the drive housing C. The drive module 440 provides driving force to the clutch drive device 400. Here, the driving force may be a rotational force that rotates the drive member 450. The drive module 440 includes a drive source 441 composed of a motor 200. The drive source 441 can receive power from the drive connector 445 and provide rotational force. The drive source 441 may also be composed of a stepper motor.

[0176] A plurality of speed-changing gears 443 may be connected to the drive source 441. The plurality of speed-changing gears 443 can reduce the rotational speed of the drive source 441 and increase the rotational force. In this embodiment, the plurality of speed-changing gears 443 includes a first speed-changing gear 443a and a second speed-changing gear 443b. The second speed-changing gear 443b can mesh and rotate with the gear 442 of the drive source 441, and the first speed-changing gear 443a can mesh with the drive gear 455 of the drive member 450.

[0177] A sensing switch 446 can be connected to the drive connector 445. The sensing switch 446 can control the drive of the drive source 441. As the sensing switch 446 is turned on or off, power can be selectively supplied to the drive source 441. For example, if the sensing switch 446 is in the on state, the power supply to the drive source 441 is cut off, thereby stopping the rotation of the drive member 450.

[0178] Here, the "on" state refers to the state in which the two switch terminals 447 and 448 constituting the sensing switch 446 are in electrical contact with each other, and the "off" state refers to the state in which the two switch terminals 447 and 448 constituting the sensing switch 446 are not in electrical contact with each other. For reference, Figure 28 The image shows the two switch terminals 447 and 448 separated from each other and not in contact. Figure 29 The diagram shows the state in which the two switch terminals 447 and 448 are in contact with each other. In this embodiment, the sensing switch 446 can be turned on or off by the sensing enclosure 459 of the drive member 450. This structure will be described again below.

[0179] Next, the drive member 450 and the pusher 460 will be described. The drive member 450 has a rotation center concentric with the motor shaft 340 and is rotated by the drive source 441. The pusher 460 moves along the axial direction in conjunction with the rotation of the drive member 450, causing the clutch 410 to move along the axial direction. As described above, in this embodiment, the pusher 460 can move only linearly along the axial direction, and the drive member 450, which actuates the pusher 460, only rotates around the motor shaft 340, thereby achieving duality. In this way, the drive member 450 does not need to move linearly, and the pusher 460 does not need to rotate, thus the gear shape for linkage with the drive source 441 and the cam shape for moving the pusher 460 can be easily implemented.

[0180] The drive member 450 and the pusher 460 can be concentrically configured. In this embodiment, the drive member 450 and the pusher 460 are concentrically configured with respect to the motor shaft 340. The drive member 450 and the pusher 460 are configured to surround the motor shaft 340 and can be concentric. As described above, if the drive member 450 and the pusher 460 are concentrically configured, the clutch drive device 400 can be configured to overlap axially with the center portion of the motor 200, thus preventing the diameter of the roller rotating device 100 from increasing due to the clutch drive device 400.

[0181] The drive member 450 can be configured in the clutch drive device 400 with restricted movement along the axial direction. The push member 460 can be configured in the clutch drive device 400 with restricted rotation relative to the drive member 450. That is, the drive member 450 can only rotate, and the push member 460 can only move linearly. In conjunction with the rotational movement of the drive member 450, the push member 460 can move linearly along the axial direction.

[0182] The drive member 450 may be configured to be closer to the motor 200 in the axial direction than the pusher 460. (Refer to...) Figure 10 The drive member 450 can be configured axially, closer to the upper part of the motor 200 than the pusher 460. In this configuration, the drive member 450 can move the pusher 460 axially away from the motor 200, i.e., towards the gear assembly 300.

[0183] The driving member 450 and the pushing member 460 may be configured to overlap each other radially. (Refer to...) Figure 6 The drive member 450 and the pusher 460 are configured to be concentric and overlap each other radially. In this embodiment, the drive member 450 is configured to surround the periphery of the pusher 460. Therefore, the drive member 450 and the pusher 460 can minimize the axial height of the clutch drive device 400.

[0184] The clutch 410 can be configured to overlap radially with the drive member 450 and the pusher member 460. For example... Figure 6As shown, a portion of the clutch 410 overlaps radially with the drive member 450 and the pusher member 460. In this embodiment, a portion of the clutch 410 overlaps radially with the drive member 450 and the pusher member 460, while another portion protrudes forward and rearward from the drive member 450 and the pusher member 460 respectively, axially. Thus, the rearward-protruding portion of the protruding portion of the clutch 410 becomes the clutch gear 417 that engages with the coupler 350, while the forward-protruding portion becomes the contact support portion 413 that is pressed by the pusher member 460.

[0185] The pushing member 460 is guided by the outer peripheral surface of the driving member 450, thereby allowing it to move along the axial direction. The pushing member 460 is guided by the driving housing C and moves only linearly; in this case, it can move linearly in conjunction with the rotation of the driving member 450. In this embodiment, a driving cam 456 for guiding the pushing member 460 is provided on the outer peripheral surface of the driving member 450, and a driven cam 466 corresponding to the driving cam 456 is provided on the pushing member 460. The driving cam 456 guides the driven cam 466, thereby allowing the pushing member 460 to move linearly. Therefore, the driving cam 456 can be referred to as a guiding cam portion, and the driven cam 466 can be referred to as a lifting guiding portion. This structure will be described in detail below.

[0186] Reference Figure 13 and Figure 14 The driving member 450 will be described below. The driving member 450 may be formed in a generally annular shape or a short tube shape. The driving member 450 may include a driving body 452. The driving body 452 may be formed in an annular shape or a short tube shape. The driving body 452 is the portion with the largest diameter in the driving member 450.

[0187] The driving member 450 may be provided with a guide wall 453 with a diameter smaller than that of the driving body 452. The guide wall 453 is formed circumferentially along the driving member 450, surrounding the first driving hole 451 formed at the center. The driving cam 456 is provided on the outer peripheral surface of the guide wall 453. The outer diameter of the guide wall 453 may be less than or equal to the inner diameter of the push member 460. The push member 460 may overlap with the guide wall 453, such that the outer peripheral surface of the guide wall 453 and the inner peripheral surface of the push member 460 face each other. The guide wall 453 can be regarded as the part that guides the linear movement of the push member 460.

[0188] The inner diameter of the guide wall 453 may be larger than the outer diameter of the drive guide 435 of the second housing 430. The guide wall 453 may rotate to surround the drive guide 435. That is, the drive guide 435 is arranged radially inward and the pusher 460 is arranged radially outward, with the guide wall 453 in between.

[0189] Reference Figure 6 The diagram illustrates the configuration of the guide wall 453 disposed between the drive guide 435 and the pusher 460. A wall rotation space OS2 is formed between the drive guide 435 and the pusher 460. The guide wall 453 is disposed within the wall rotation space OS2. With this structure, the guide wall 453 of the drive member 450 can rotate between the drive guide 435 and the pusher 460.

[0190] In addition, such as Figure 6 As shown, the action space OS1 formed between the guide wall 453 and the inner main body 425 of the first housing 420 can be equipped with the pusher 460. Therefore, the pusher 460 can move linearly between the guide wall 453 and the inner main body 425 of the first housing 420.

[0191] Refer again Figure 13 A drive gear 455 can be arranged circumferentially along the drive body 452. The drive gear 455 can mesh and rotate with the first transmission gear 443a connected to the drive source 441. The drive gear 455 is continuously arranged circumferentially on the outer peripheral surface of the drive body 452. Therefore, the drive member 450 can rotate continuously in a first direction. Here, the first direction is... Figure 15 The counterclockwise direction is the reference point.

[0192] A drive cam 456 is provided on the surface of the guide wall 453, the axial distance of which varies along the circumference of the guide wall 453. The drive cam 456 can raise or lower the pusher 460 during the rotation of the drive member 450. At this time, the drive cam 456 and the elastic member S can work together to lower the pusher 460. The specific structure of the drive cam 456 will be described again below.

[0193] A sensing enclosure 459 may be provided circumferentially along the edge of the driving member 450. The sensing enclosure 459 may be provided along the edge of the driving body 452. The sensing enclosure 459 may protrude axially from the edge of the driving body 452. The axial height of the sensing enclosure 459 may be different from the axial height of the driving gear 455.

[0194] At the edge of the drive member 450, a sensing avoidance portion 452a, omitting the sensing enclosure 459, can be formed along the circumference of the drive member 450. Alternatively, the sensing avoidance portion 452a can be viewed as being disposed between two spaced-apart sensing enclosures 459. (Refer to...) Figure 18 The sensing avoidance portion 452a is formed between the end portions 459' and 459" of two sensing enclosures 459 that are spaced apart from each other. As a result, the sensing enclosures 459 and the sensing avoidance portions 452a are alternately arranged circumferentially along the edge of the drive member 450.

[0195] During the rotation of the drive member 450, the sensing enclosure 459 interferes with the switching device, thereby turning the sensing switch 446 on or off. The sensing enclosure 459 also interferes with one of the two switching terminals 447 and 448 constituting the sensing switch 446, thus pushing one of the switching terminals 447 and 448 towards the other. In this embodiment, the sensing enclosure 459 interferes with the first switching terminal 447 of the switching terminals 447 and 448, which is radially closer to the drive member 450. Reference numeral 447a indicates a sensing interference portion 447a protruding radially from the first switching terminal 447 along the drive member 450, with the sensing enclosure 459 interfering with the sensing interference portion 447a.

[0196] The driving member 450 may be provided with the same number of the sensing enclosures 459 and the driving cams 456. In this embodiment, the driving member 450 is provided with two sensing enclosures 459 and two driving cams 456. The sensing enclosures 459 confirm the driving state (rotation state) of the driving cams 456 to activate the sensing switch 446, and therefore are preferably provided in the same number as the driving cams 456.

[0197] A lifting space 454a, which serves as an empty space, can be formed between the guide wall 453 and the sensing wall 459. The pusher 460 can be disposed in the lifting space 454a, and the pusher 460 can move axially within the lifting space 454a. (Refer to...) Figure 18The lifting space 454a opens forward but is blocked at the rear by the base plate 454. One end of the pusher 460 may be mounted on the base plate.

[0198] The pusher 460 is described as being configured to surround the guide wall 453. A driven cam 466 corresponding to the drive cam 456 may be provided on the outer peripheral surface of the pusher 460 facing the guide wall 453. The driven cam 466 moves along the drive cam 456, thereby causing the pusher 460 to move the clutch 410.

[0199] A ring-shaped or short-tube-shaped actuating body 462 can form the skeleton of the actuating member 460. The actuating body 462 has an inner diameter larger than the outer diameter of the guide wall 453. The actuating body 462 has a structure surrounding the second driving hole 461. The actuating body 462 can form a continuous path connecting the second driving hole 461 to the first driving hole 451 of the driving member 450.

[0200] The driven cam 466 may be provided on the inner circumferential surface of the pushing body 462. The driven cam 466 is the part that moves along the driving cam 456 and may have a structure that protrudes radially inward from the inner circumferential surface of the pushing body 462. The driven cam 466 extends circumferentially along the pushing body 462. The specific structure of the driven cam 466 will be described again below.

[0201] The pushing body 462 may be provided with an anti-rotation protrusion 469a. The anti-rotation protrusion 469a prevents the pushing member 460 from rotating. The anti-rotation protrusion 469a is inserted into an anti-rotation groove 425a formed in the drive housing C. The anti-rotation protrusion 469a is inserted into the anti-rotation groove, thereby interfering in the direction of rotation. Thus, the anti-rotation protrusion 469a can move only in the direction of vertical movement along the anti-rotation groove, i.e., the front-to-back direction.

[0202] The anti-rotation protrusion 469a can protrude radially outward from the edge of the pushing body 462. In this embodiment, the anti-rotation protrusion 469a is disposed at the lower rearward end of the pushing body 462. A plurality of the anti-rotation protrusions 469a can be configured to be spaced apart from each other along the outer peripheral surface of the pushing body 462.

[0203] For reference only. Figure 19Reference numeral 469 in the accompanying drawings indicates a guide rib 469 protruding radially outward along the outer peripheral surface of the push body 462. The guide rib 469 may have an arc shape surrounding the outer peripheral surface of the push body 462. The guide rib 469 may reduce the gap between the push member 460 and the inner main body portion 425 of the first housing 420. In this way, when the push member 460 moves axially in the front-rear direction, the push member 460 can move stably without tilting to one side.

[0204] Reference Figure 15 This shows the state in which the clutch drive unit 400 is assembled. To aid understanding, Figure 15 The first housing 420 is indicated by a dashed line. When the pusher 460 is engaged with the drive member 450, the guide wall 453 of the drive member 450 is not visible because it is covered by the pusher 460. In this state, if the drive member 450 rotates, the pusher 460 moves in a front-to-back direction (up and down relative to the figure). At this time, due to the anti-rotation groove 425a, the pusher 460 can move only in a straight line without rotating.

[0205] More specifically, even though the pusher 460 covers the guide wall 453 of the drive member 450, the drive gear 455 of the drive member 450 is exposed radially. This exposed drive gear 455 can mesh with the first transmission gear 443a. Therefore, the rotational force of the drive source 441 is transmitted to the drive gear 455. At this time, the sensing wall 459 is provided on the drive member 450, but the axial height of the drive gear 455 is different from the axial height of the sensing wall 459; therefore, the sensing wall 459 does not interfere with the meshing between the drive gear 455 and the first transmission gear 443a.

[0206] For reference only. Figure 15 Clutch 410 is omitted in the figure. Based on the figure, clutch 410 can be moved from top to bottom and inserted into the center of the clutch drive device 400. In this way, the pushing surface 462a of the forward-exposed pusher 460 can push clutch 410 forward.

[0207] Figure 16 It is to remove the second housing 430 and the drive member 450, and from the... Figure 15 The clutch drive device 400 is shown in the opposite direction. It can be seen that a driven cam 466 is provided on the inner circumferential surface of the pusher 460, and the driven cam 466 protrudes radially inward. Figure 16The diagram shows the anti-rotation protrusion 469a of the pusher 460 inserted into the anti-rotation groove 425a. As can be seen, in this embodiment, the two anti-rotation protrusions 469a are disposed on the outer peripheral surface of the pusher 460 with a phase difference of 180 degrees from each other. In this state, the pusher 460 can move forward (downward, relative to the figure). The omitted second housing 430 can support the pusher 460 from the rear.

[0208] Figure 17 The diagram shows the shape of the drive member 450 with the first housing 420 removed, indicated by dashed lines. If the drive member 450 is rotated by the drive source 441 in the direction of arrow ①, the drive cam 456 pushes the driven cam 466. Consequently, the pusher 460 moves in the direction of arrow ②. During this movement, the pusher 460 axially pushes the clutch 410, thereby disengaging the clutch 410.

[0209] Figure 17 This is the state where the first switch terminal 447 and the sensing enclosure 459 do not interfere. The sensing interference portion 447a of the first switch terminal 447 is disposed in the sensing avoidance portion 452a, so that the sensing interference portion 447a of the first switch terminal 447 is in a state of protruding radially inward toward the driving member 450. If the driving member 450 continues to rotate in the direction of arrow ①, the interval of the sensing avoidance portion 452a ends, and the sensing enclosure 459 interferes with the sensing interference portion 447a, thereby pushing the sensing interference portion 447a radially outward. This process will be explained again below.

[0210] Figure 18 The clutch 410, drive member 450, and pusher 460 are shown in their disengaged state. Although not shown, it is understood that... Figure 18 Based on this, an elastic member S can be disposed at the lower part of the clutch 410, thereby allowing the clutch 410 to be pushed rearward (above the reference figure). Therefore, the clutch 410 is essentially in a rearward-pushed state. Here, the rearward-pushed state of the clutch 410 is the same as the engaged state when engaged with the coupler 350.

[0211] like Figure 18As shown, the diameter of the contact support portion 413 of the clutch 410 can be larger than the outer diameter of the pusher 460. Simultaneously, the outer diameter of the clutch body 412 can be smaller than the second drive hole 461 of the pusher 460. In this way, the clutch body 412 can be inserted into the second drive hole 461, and the contact support portion 413 is engaged with the edge of the second drive hole 461. Therefore, the contact support portion 413 applies pressure to the surface of the pusher 460 corresponding to the edge of the second drive hole 461.

[0212] Figure 19 The diagram shows the drive member 450 and the pusher 460 separated from each other. It is thus evident that the drive cam 456 is arranged circumferentially on the outer peripheral surface of the guide wall 453. In this embodiment, two drive cams 456 are arranged on the outer peripheral surface of the guide wall 453 with a 180-degree phase difference. Alternatively, the drive cam 456 may consist of one or more cams.

[0213] The drive cam 456 may include a plurality of intervals in which the axial length varies along the circumference of the drive member 450. Since the drive cam 456 includes a plurality of intervals in which the axial length varies along the circumference of the drive member 450, the axial movement distance of the push member 460 can vary according to the rotation angle of the drive member 450.

[0214] The plurality of said intervals may include a push-release interval RS extending circumferentially along the drive cam 456. The push-release interval RS can be considered as an omitted interval of the drive cam 456. If the driven cam 466 enters the push-release interval RS, the axial relative distance between the pusher 460 and the drive member 450 is at its shortest. That is, if the driven cam 466 is positioned in the push-release interval RS, the drive member 450 is in a state where it is not pushing the pusher 460 forward.

[0215] The plurality of said intervals may include a pushing action interval OS. The pushing action interval OS may extend circumferentially along the drive cam 456. The pushing action interval OS can be considered as the interval in which the drive cam 456 is formed on the guide wall 453. The pushing action interval OS protrudes further forward in the axial direction than the pushing release interval RS, opposite to the rotor 230, thereby pushing the pusher 460 forward.

[0216] The pushing action range OS may include a pushing drive portion 457a that pushes the pusher 460 in a direction spaced apart from the rotor 230. The pushing drive portion 457a, as part of the drive cam 456, may extend in an inclined direction in the circumferential direction. The pushing drive portion 457a may form an inclined path from the base plate portion 454 of the drive member 450 to the pushing retaining portion 458 described later. The pushing drive portion 457a may be referred to as a first cam portion, and the pushing retaining portion 458 may be referred to as a second cam portion.

[0217] The push drive section 457a can gradually increase in height towards the push holding section 458 from the push release interval RS in a direction opposite to the rotation direction of the drive cam 456. The driven cam 466 can move forward in the direction that gradually increases along the push drive section 457a. In this way, as the driven cam 466 moves along the drive cam 456, the force used to overcome the elastic force of the elastic member S can be dispersed.

[0218] The drive unit 457a may have a continuous curved or inclined surface structure connecting the start position 457a' and the end position 457a" of the drive unit 457a. In this embodiment, the start position 457a' and the end position 457a" of the drive unit 457a have a continuous inclined surface structure. As another example, the drive unit 457a may also be composed of a plurality of parts with different inclination angles.

[0219] The pushing action range OS may include a pushing holding portion 458 that keeps the pushing member 460 separated from the rotor 230. The pushing holding portion 458 includes a start position and an end position, and may form a continuous planar structure between the start position and the end position. At this time, the start position 457a” of the pushing holding portion 458 is the same as the end position 457a” of the pushing drive portion 457a. The end position 457b’ of the pushing holding portion 458 is the same as the start position 457b’ of the release drive portion 457b, which will be described later.

[0220] Unlike the drive unit 457a, the retaining unit 458 may have a constant height relative to the axial direction, instead of extending in an inclined direction along the circumference. This way, during the circumferential movement of the separating retaining unit 468 of the driven cam 466 along the retaining unit 458, no axial movement of the pusher 460 occurs. Alternatively, the retaining unit 458 may also have a structure that is inclined relative to the axial direction and does not have a constant height. However, the inclination angle of the retaining unit 458 may be more gradual than that of the drive unit 457a.

[0221] The push-holding portion 458 can extend circumferentially along the drive member 450. The push-holding portion 458 can form a maximum distance in the axial direction opposite to the rotor 230. That is, if the separation holding portion 468 of the driven cam 466 is disposed on the push-holding portion 458, the pusher 460 can be in a state that pushes the clutch 410 away from the rotor 230 to the maximum extent, i.e., in a disengaged state.

[0222] The push action range OS may include a release drive unit 457b. When the clutch 410 switches from the disengaged state to the engaged state, the driven cam 466 moves along the release drive unit 457b. The driven cam 466 can move along the release drive unit 457b and enter the push release range RS.

[0223] The release drive portion 457b can be formed in a direction inclined circumferentially along the drive member 450. More precisely, the release drive portion 457b can gradually decrease in height towards the push release range RS along the rotation direction of the drive cam 456. This inclined structure can disperse the elastic force of the elastic member S when the push member 460 releases from the state of pushing the clutch 410 forward. The inclined structure of the release drive portion 457b can prevent the push member 460 from colliding with the drive member 450 at high speed due to the elastic force of the elastic member S.

[0224] The release drive portion 457b can be disposed on the opposite side of the push drive portion 457a with the push holding portion 458 as the center. That is, with the push holding portion 458 as the center, the release drive portion 457b has a position symmetrical to the push drive portion 457a. In this way, with Figure 19 Based on this, the driven cam 466 can rise along the push drive section 457a and enter the push holding section 458, and then fall again along the release drive section 457b.

[0225] As described above, the push action range OS, namely the push drive part 457a, the push holding part 458, and the release drive part 457b constituting the drive cam 456, can form a continuous guide path that causes the push member 460 to rise-hold-fall.

[0226] The push release interval RS and the push action interval OS can be repeated circumferentially along the drive cam 456. In this way, when the drive member 450 rotates continuously in one direction, the push member 460 can cause the clutch 410 to alternately switch between disengaged and engaged states, and the drive source 441 only needs to cause the drive member 450 to rotate in one direction.

[0227] The circumferential length of the push drive portion 457a can be longer than the circumferential length of the release drive portion 457b. If the push drive portion 457a forms a section longer than the release drive portion 457b, the external force applied when the moving clutch 410 needs to switch to the disengagement state can be distributed. At the same time, the relatively short release drive portion 457b allows the clutch 410 to switch from the disengagement state to the engagement state more quickly.

[0228] Referring to the driven cam 466, the driven cam 466 can be disposed on the inner circumferential surface of the pusher 460. The driven cam 466 can be disposed circumferentially on the inner circumferential surface of the pusher 460. In this embodiment, two driven cams 466 can be disposed on the inner circumferential surface of the pusher 460 with a phase difference of 180 degrees. As another example, the driven cam 466 can also be composed of one or more.

[0229] The driven cam 466 may include a clutch locking section SS extending circumferentially. The clutch locking section SS is the section used to form an engaged state in which the pusher 460 pushes the clutch 410 to engage the clutch 410 with the coupler 350. In other words, the clutch locking section SS can also be regarded as the section in the driven cam 466 where the clutch disengagement section CS is omitted.

[0230] The driven cam 466 is configured such that its axial protrusion length in the clutch locking range SS is shorter than that in the clutch disengagement range CS. Therefore, the pusher 460 can be configured to be axially closer to the drive member 450 in the clutch locking range SS, and the axial pushing state of the clutch 410 can also be released.

[0231] The clutch disengagement zone CS extends circumferentially along the driven cam 466. The clutch disengagement zone CS protrudes further axially toward the rotor 230 than the clutch locking zone SS. If the clutch disengagement zone CS is guided by the actuation zone OS of the drive cam 456, the actuator 460 can move the clutch 410 in a direction spaced apart from the rotor 230.

[0232] From the structure of the clutch disengagement zone CS, as... Figure 19 As shown, the clutch disengagement range CS may include a disengagement drive portion 467a whose height gradually increases circumferentially from the clutch locking range SS toward the disengagement holding portion 468. The height of the disengagement drive portion 467a gradually changes circumferentially. The disengagement drive portion 467a is the portion that rises along the push drive portion 457a of the drive member 450. For this purpose, the disengagement drive portion 467a may be configured to face the push drive portion 457a circumferentially.

[0233] The separation drive unit 467a may have a continuous curved or inclined surface structure connecting the start position 467a' and the end position 467a" of the separation drive unit 467a. In this embodiment, the start position 467a' and the end position 467a" of the separation drive unit 467a have a continuous inclined surface structure. As another example, the separation drive unit 467a may also be composed of a plurality of parts with different inclination angles.

[0234] In this embodiment, the drive cam 456 has a push drive portion 457a with a first tilt angle relative to the drive member 450 in the circumferential direction, and the separation drive portion 467a has the same tilt angle relative to the push member 460 in the circumferential direction as the first tilt angle. Alternatively, the push drive portion 457a and the separation drive portion 467a may have different tilt angles than each other.

[0235] The separation drive portion 467a can be parallel to the push drive portion 457a of the drive cam 456. In this way, the separation drive portion 467a can rise along the push drive portion 457a in a state of surface contact with the push drive portion 457a of the drive cam 456. Therefore, the elastic force of the elastic member S is more widely distributed, allowing the push member 460 to move stably along the axial direction.

[0236] The clutch disengagement range CS may include the disengagement holding portion 468. The disengagement holding portion 468 may extend circumferentially along the pusher 460, forming a maximum distance axially toward the rotor 230. Unlike the disengagement drive portion 467a, the disengagement holding portion 468 may have a constant height relative to the axial direction, rather than extending in a circumferentially inclined direction. In this way, during the circumferential movement of the disengagement holding portion 468 of the driven cam 466 along the pusher holding portion 458, no axial movement of the pusher 460 occurs. Alternatively, the disengagement drive portion 467a may also have a structure that is inclined relative to the axial direction and does not have a constant height. However, the inclination angle of the disengagement drive portion 467a is formed more gently than that of the disengagement drive portion 467a.

[0237] The separation holding portion 468 can extend circumferentially along the push member 460. The separation holding portion 468 can form a maximum distance in the axial direction opposite to the rotor 230. That is, if the separation holding portion 468 of the driven cam 466 is disposed on the push holding portion 458, the push member 460 can be in a state that pushes the clutch 410 away from the rotor 230 to the maximum extent.

[0238] The separation holding portion 468 can be parallel to the push holding portion 458 of the drive cam 456. In this way, the separation holding portion 468 can be stably supported while in contact with the push holding portion 458. Figure 25 This form is shown in the image.

[0239] The clutch disengagement zone CS may further include a locking drive unit 467b. The locking drive unit 467b may be disposed on the opposite side of the push drive unit 457a, separated from the disengagement holding unit 468. That is, with the disengagement holding unit 468 as the center, the locking drive unit 467b is disposed in a position symmetrical to the disengagement drive unit 467a. In this way, with... Figure 19 Based on this, the driven cam 466 can rise along the push drive 457a and enter the push holding part 458, and then the locking drive 467b descends again along the release drive 457b.

[0240] The locking drive unit 467b may have a structure in which the height gradually decreases towards the clutch locking range SS. To move the clutch 410 from the disengaged state to the engaged state, the locking drive unit 467b may move along the release drive unit 457b of the drive cam 456. The locking drive unit 467b has the same tilt angle as the release drive unit 457b, thus allowing it to move relative to the clutch in a face-to-face contact state.

[0241] The separation drive section 467a can be longer in circumferential length along the pusher 460 than the locking drive section 467b. If the separation drive section 467a forms a longer section than the locking drive section 467b, the external force applied to the moving clutch 410 during the separation state switching, which requires greater force, can be distributed. Simultaneously, the relatively shorter locking drive section 467b allows the clutch 410 to switch from the disengaged state to the engaged state more quickly.

[0242] The length of the push-release interval RS of the drive member 450, based on its circumference, can be configured to be longer than the length of the separation holding portion 468 of the push member 460, based on its circumference. If the push-release interval RS is longer than the separation holding portion 468, the separation holding portion 468 can move a further constant distance along the push-release interval RS. In this way, the distance the separation holding portion 468 moves along the push-release interval RS can become the interval used to compensate for overrun when the drive member 450 is not precisely controlled and overrun occurs.

[0243] If the separation holding portion 468 enters the push-release range RS of the drive member 450, then the drive member 450 and the pusher 460 can have a minimum separation distance along the axial direction. When the separation holding portion 468 enters the push-release range RS, the drive member 450 and the pusher 460 can become closest in the axial direction. If the separation holding portion 468 enters the push-release range RS, then as Figure 23 As shown, the separation holding portion 468 of the pusher 460 contacts the base plate portion 454 of the drive member 450, allowing the drive member 450 and the pusher 460 to become closest in the axial direction. Thus, the clutch 410 can be switched to the engaged state.

[0244] During the period when the drive member 450 further rotates by a margin angle from the position where the separation holding part 468 enters the push release interval RS, the minimum separation distance can be maintained. In this embodiment, the separation holding part 468 can further rotate a constant distance within the push release interval RS. At this time, the angle by which the separation holding part 468 further rotates within the push release interval RS is called the margin angle. This margin angle can compensate for overtravel when the drive member 450 is not precisely controlled and overtravel occurs. For example, even if the drive member 450 fails to stop in time and rotates further at the instant the separation holding part 468 enters the push release interval RS, the separation drive part 467a can be prevented from rising again along the push drive part 457a because the separation holding part 468 rotates within the push release interval RS.

[0245] The circumferential length of the push-release interval RS of the drive member 450 can be longer than the circumferential length of the clutch disengagement interval CS of the push member 460. This ensures that even if the entire clutch disengagement interval CS, i.e., the entire driven cam 466, is disposed within the push-release interval RS, a sufficient margin of distance can be maintained between the driven cam 466 and the push-release interval RS. This margin of distance can compensate for the overtravel of the drive member 450.

[0246] The circumferential length of the pushing action range OS of the drive member 450 can be longer than the circumferential length of the clutch disengagement range CS of the push member 460. That is, the total circumferential distance of the drive cam 456 is longer than the total circumferential distance of the driven cam 466. If the circumferential length of the drive cam 456 is longer, the driven cam 466 can ensure a longer guiding distance that can be guided by the drive cam 456. Therefore, it is possible to prevent the drive member 450 from switching back to the engagement state after entering the disengagement state where the disengagement holding part 468 is placed on the push holding part 458 and overtravel occurs, if it cannot stop immediately.

[0247] Reference Figure 20 The arrow indicates the rotation direction of the drive member 450. The drive gear 455 of the drive member 450 can receive rotational force from the drive source 441 and rotate continuously in the first direction (arrow direction). In this embodiment, the drive member 450 only rotates and stops in the first direction. That is, the drive source 441 does not need to rotate the drive member 450 in the second direction, which is the opposite direction. This is because the push drive part 457a, the push holding part 458, and the release drive part 457b, which are included in the push action range OS of the drive member 450, are continuously formed in the circumferential direction, forming the lifting path of the push member 460.

[0248] like Figure 20 As shown, the sensing avoidance portion 452a is formed between the end portions 459' and 459" of two sensing enclosures 459 that are spaced apart from each other. The sensing enclosures 459 and the sensing avoidance portions 452a are arranged alternately in the circumferential direction along the edge of the drive member 450.

[0249] Reference Figure 21 The driven cam 466 of the pusher 460 can be composed of a plurality of parts having different heights along the axial direction of the pusher 460. As mentioned above, a separation drive part 467a and a locking drive part 467b are provided on both sides with the separation holding part 468 as the center. As shown in the figure, in this embodiment, the separation drive part 467a has a gentler tilt angle than the locking drive part 467b.

[0250] The separation drive unit 467a includes a start position 467a' and an end position 467a'. The start position 467a' and end position 467a' of the separation drive unit 467a can be close to or opposite to the start position 457a' and end position 457a' of the push drive unit 457a, respectively. If the separation drive unit 467a rises along the push drive unit 457a, the start position 467a' of the separation drive unit 467a is separated from the push drive unit 457a, but the end position 467a' of the separation drive unit 467a can move along the inclined surface of the push drive unit 457a. Furthermore, at the instant when the end position 467a” of the separation drive part 467a connects with the end position 457a” of the push drive part 457a, that is, at the instant when it is placed in the push holding part 458, the push member 460 has the maximum protrusion distance.

[0251] Reference Figure 22 The diagram shows the rotation of the drive member 450 and the sensing switch 446 that operates according to the rotation of the drive member 450 in a top view. If the gear 442 of the drive source 441 rotates in the direction of arrow ①, then the plurality of gears 443 rotate in conjunction with it in the direction of arrow ②. The drive gear 455, which meshes with the plurality of gears 443, rotates in the direction of arrow ③ by the plurality of gears 443. At this time, the center of rotation of the drive gear 455 becomes the center of the first drive hole 451 formed in the center of the drive member 450.

[0252] If the drive gear 455 rotates, the drive cam 456 can push the driven cam 466 axially to raise or lower the pusher 460. As mentioned above, the lowering of the pusher 460 can be achieved by means of the elastic force of the elastic member S.

[0253] In order to sense the movement of the pusher 460 along with the movement of the pusher 460, the sensing switch 446 can be linked to the drive member 450. For example... Figure 22 As shown, the sensing enclosure 459 of the driving member 450 can rotate with the rotation of the driving member 450, thereby bringing it closer to the sensing switch 446. More precisely, of the two switch terminals 447 and 448 constituting the sensing switch 446, the sensing interference portion 447a provided at the first switch terminal 447 can interfere with the sensing enclosure 459. Figure 22This indicates the state of the sensing interference part 447a, which is disposed between two adjacent sensing enclosures 459 to form a sensing avoidance part 452a, before it is pressed radially (in the direction of arrow ④) by the sensing enclosure 459.

[0254] If the sensing interference part 447a is pressed by the sensing enclosure 459, the two switch terminals 447 and 448 will make electrical contact with each other. Figure 29 This state is illustrated in the diagram. If the two switch terminals 447 and 448 are in electrical contact with each other and the sensing switch 446 is in the open state, the control unit can stop the drive of the drive source 441. As a result, the rotation of the drive member 450 can stop, and the pusher 460 can maintain its current position. For example, the pusher 460 can protrude a maximum distance axially, thereby maintaining the position in which the clutch 410 is disengaged.

[0255] If the sensing switch 446 is in the ON state, the control unit can cut off the power supply to the drive source 441, thereby stopping the rotation of the drive member 450. Alternatively, if the sensing switch 446 is in the OFF state, the control unit can cut off the power supply to the drive source 441, thereby stopping the rotation of the drive member 450. That is, the control unit can stop the drive of the drive source 441 when the sensing switch 446 changes from the ON state to the OFF state or from the OFF state to the ON state.

[0256] Figures 23 to 25 The process of rotating the drive member 450, which constitutes an embodiment of the present invention, to raise the pusher member 460 is shown in sequence. Figure 23 The pusher 460 is in a state where it does not protrude axially from the drive member 450. The separation holding portion 468 of the pusher 460 contacts the base plate portion 454 of the drive member 450, thereby bringing the drive member 450 and the pusher 460 into the closest possible position axially. At this time, the pusher 460 does not push the clutch 410 axially, so the clutch 410 can be engaged with the coupler 350, and the garment processing device can be in spin-drying mode.

[0257] If the driving member 450 rotates, then it is in the position of Figure 24 The state shown. If the drive member 450 rotates, the push drive portion 457a of the drive cam 456 provided on the drive member 450 can push up the driven cam 466. Thus, the separation holding portion 468 of the push member 460 is separated from the base plate portion 454 of the drive member 450. For reference, Figure 24This indicates that the starting position 457a' of the drive unit 457a pushes the driven cam 466, thereby moving the push member 460 forward by the maximum travel distance D (refer to...). Figure 25 () is in a state of 1 / 2.

[0258] If the driving member 450 rotates further from this state in the same direction, then as Figure 25 As shown, the pusher 460 moves forward a maximum distance D, and due to the pusher 460, the clutch 410 also moves forward. More precisely, while the drive member 450 rotates in the direction of arrow ①, the pusher 460 is lifted in the direction of arrow ②. At this time, the separation holding portion 468 of the pusher 460 contacts the end position 457a” of the push drive portion 457a, which is the start position 457a” of the push holding portion 458. That is, the separation holding portion 468 of the pusher 460 enters the push holding portion 458.

[0259] Figures 26 to 29 The process of rotating the drive member 450, which constitutes an embodiment of the present invention, to raise the pusher member 460 is shown in sequence. Figures 26 to 29 The diagram progressively illustrates the continuous rotation of the driving member 450 in the first direction (arrow ①). For reference, Figure 26 This is the state in which the driving cam 456 and the driven cam 466 are separated from each other. Figure 27 The drive cam 456 is in a state where it meets the driven cam 466. Figure 28 This is the state in which the driving cam 456 causes the driven cam 466 to lift forward by the maximum distance. Figure 29 This indicates that the driving component 450 is from Figure 28 The state is further rotated into a new form.

[0260] Reference Figure 26 The push drive portion 457a of the drive cam 456 and the disengagement drive portion 467a of the driven cam 466 are circumferentially spaced apart from each other. Referring to the lower side of arrow ①, the disengagement drive portion 467a of the driven cam 466 is separated from the push drive portion 457a of the drive cam 456 in a counterclockwise direction. Therefore, in order for the push drive portion 457a of the drive cam 456 to push up the disengagement drive portion 467a of the driven cam 466, the drive member 450 needs to rotate in a counterclockwise direction (in the direction of arrow ①).

[0261] Reference Figure 27This indicates that the push drive portion 457a of the drive cam 456 and the disengagement drive portion 467a of the driven cam 466 are facing each other. That is, they are in a state where the push drive portion 457a of the drive cam 456 and the disengagement drive portion 467a of the driven cam 466 are in close contact with each other. However, the push drive portion 457a is not yet in a state where it pushes up the disengagement drive portion 467a.

[0262] In this state, if the driving member 450 rotates further in a counterclockwise direction (arrow ① direction), it is in... Figure 28 In that state, the pushing drive portion 457a of the driving member 450 penetrates the lower part of the separating drive portion 467a of the pushing member 460 and pushes up the separating drive portion 467a. During this process, the entire pushing member 460 can move forward (in the direction of arrow ②). As the pushing member 460 moves forward, the pushing surface 462a of the pushing member 460 also moves forward. Figure 28 The clutch 410 is omitted, but the pushing surface 462a of the pusher 460 can move the clutch 410 to the disengaged state in a state of contact with the clutch 410.

[0263] Reference Figure 28 The separation drive portion 467a of the pusher 460 rises along the push drive portion 457a of the drive member 450, thereby reaching a state where the end position 457a” of the push drive portion 457a and the end position 467a” of the separation drive portion 467a meet each other. At this time, the pusher 460 has moved the maximum distance.

[0264] In this state, the drive member 450 can rotate further in a counterclockwise direction (arrow ① direction). Figure 29 As can be seen, the push-hold portion 458 of the push member 460 is positioned above the push-hold portion 458 of the drive member 450. The push-hold portion 458 and the push-hold portion 468 have the same height in the circumferential direction, so even if the drive member 450 is rotated further in the counterclockwise direction (arrow ① direction), the height of the push member 460 will not change.

[0265] The push-holding portion 458 and the separation-holding portion 468 are configured as corresponding planes, allowing the push member 460 to remain stably positioned in the push-holding portion 458. At this time, the elastic member S can also apply an elastic force downward to the push member 460 via the clutch 410, but the push-holding portion 458 and the separation-holding portion 468 can be in surface contact with each other, thus allowing the push member 460 to be stably supported by the drive member 450.

[0266] If in Figure 28 In that state, the control unit stops the rotation of the drive member 450; however, if overtravel occurs, the drive member 450 and the pusher 460 may also be in a state of... Figure 29 That state. However, in this embodiment, the contact interval between the push holding part 458 and the separation holding part 468 is ensured to be long enough so that even if overtravel occurs, the push member 460 can be prevented from descending again.

[0267] Figure 30 This illustrates the deployed state of the drive cam 456 of the drive member 450, the sensing enclosure, and the driven cam 466 of the pusher 460, constituting an embodiment of the present invention. More precisely, Figure 30 The driving member 450 and the pushing member 460 are fully extended, and the driving cam 456, the sensing enclosure 459, and the driven cam 466 are shown in planar form. Arrow ① indicates the rotation direction of the driving member 450, and arrow ② indicates the forward movement of the pushing member 460.

[0268] Figure 30 The dashed line represents the drive cam 456 of the drive member 450, and the dotted line represents the sensing enclosure 459 of the drive member 450. The solid line represents the driven cam 466 of the pusher member 460. For reference, Figure 30 When the push drive unit 457a pushes up the separation drive unit 467a, the push member 460 moves forward (in the direction of arrow ②), and the push member 460 has moved 1 / 2 of the maximum moving distance.

[0269] Figure 30 In the accompanying drawings, reference numeral "A" indicates the starting position of the push-release interval RS of the drive member 450, which is the lowest position of the release drive section 457b. Reference numeral "B" indicates the ending position of the push-release interval RS of the drive member 450, which is the starting position 467a' of the separation drive section 467a, which is the lowest point of the push drive section 457a.

[0270] Reference numeral "C" indicates the end position 467a of the separation drive portion 467a of the pusher 460; reference numeral "D" indicates the end position of the push holding portion 458 of the drive member 450, which is also the beginning position of the release drive portion 457b; reference numeral "E" indicates the end position of the release drive portion 457b; and there may be a 180-degree phase difference between A and E.

[0271] Reference numeral "①" indicates the upper position of the locking drive unit 467b, which is one end of the clutch disengagement zone CS. Reference numeral "②" indicates the end position of the clutch locking zone SS, which is the same as the upper position of the locking drive unit 467b. There can be a 180-degree phase difference between ① and ②.

[0272] Here, reference numerals A, B, D, and E indicate positions that move circumferentially (in the direction of arrow ①) as the drive member 450 rotates, while C, ①, and ② indicate positions that are fixed regardless of the rotation of the drive member 450. This is because C, ①, and ② represent the positions of the driven cam 466 of the push member 460, which does not rotate.

[0273] Figure 30 S1 is the AB interval, which is the push release interval RS. S2 is the BC interval, which is the interval in the push action interval OS where the push drive unit 457a is formed. S3 is the CD interval, which is a part of the clutch locking interval SS. S4 is the DE interval, which is the interval in the push action interval OS where the release drive unit 457b is formed.

[0274] Here, the pushing action range OS in which the driving member 450 causes the pushing member 460 to rise or fall is the same as the BE range. Additionally, the clutch disengagement range CS in which the pushing member 460 causes the clutch 410 to rise or fall is ①-C, and the clutch locking range SS in which the pushing member 460 does not drive the clutch 410 is C-②.

[0275] Figure 30 T1 is the region where the sensing avoidance portion 452a is formed, and T2 is the region with the sensing enclosure 459. The center line representing the 180-degree phase is at the same position as the sensing interference portion 447a of the first switch terminal 447. The position of the sensing interference portion 447a is fixed. Therefore, if one end 459' of the sensing enclosure 459 reaches the 180-degree phase during the rotation of the drive member 450, the sensing enclosure 459 encounters the sensing interference portion 447a. The sensing enclosure 459 presses against the sensing interference portion 447a, thereby turning the sensing switch 446 into the open state, and the control unit stops the rotation of the drive member 450.

[0276] Reference Figures 31 to 34 This section explains the operation of the driving cam 456, the driven cam 466, and the sensing wall 459. First, refer to... Figure 31 The driving portion 457a of the driving cam 456 and the separating portion 467a of the driven cam 466 are in a state where they are in close contact with each other. However, Figure 30The image shows the state where the drive cam 456 has not yet pushed up the driven cam 466. Additionally, one end 459' of the sensing enclosure 459 is circumferentially separated from the sensing interference portion 447a (in the direction of arrow ①).

[0277] Figure 32 It shows Figure 31 The drive member 450 rotates circumferentially (in the direction of arrow ①). The push drive portion 457a of the drive member 450 penetrates the lower part of the separation drive portion 467a of the driven cam 466, thereby pushing up the push member 460. Figure 32 As shown, the end position 457a” of the pushing drive unit 457a and the end position 467a” of the separating drive unit 467a are in a state of meeting each other. At this point in time, the pushing member 460 can move the maximum separation distance along the axial direction, that is, forward (in the direction of arrow ②).

[0278] Figure 32 The diagram illustrates the configuration where one end 459' of the sensing enclosure 459 encounters the sensing interference portion 447a. If the pusher 460 moves the maximum axial distance, the rotation of the drive member 450 needs to be stopped. Therefore, at this point, one end 459' of the sensing enclosure 459 presses against the sensing interference portion 447a to turn the sensing switch 446 into the open state. In this embodiment, from the point where one end 459' of the sensing enclosure 459 encounters the sensing interference portion 447a, the drive member 450 further rotates by a predetermined angle so that the surface of the sensing enclosure 459 can fully press against the sensing interference portion 447a.

[0279] As described above, in this embodiment, the control unit can be positioned at the point in time when the separation holding portion 468 of the pusher 460 enters the push holding portion 458 of the drive member 450. Figure 32 The rotation of the drive member 450 is stopped (in the state of...). Alternatively, the control unit may stop the rotation of the drive member 450 after the drive member 450 has rotated a predetermined angle or a buffer time, starting from the point when the separation holding portion 468 of the pusher 460 enters the push holding portion 458 of the drive member 450. This is because a margin angle is ensured in this embodiment.

[0280] Reference Figure 33 The driving member 450 is in a position from Figure 31The position is further rotated in the circumferential direction (arrow ① direction). During this process, the separation holding portion 468 of the pusher 460 moves along the push holding portion 458 of the drive member 450. At this time, the separation holding portion 468 and the push holding portion 458 have the same height in the circumferential direction (arrow ① direction), so no axial movement of the pusher 460 occurs during this process.

[0281] Figure 33 In this process, the sensing enclosure 459 remains overlapping with the sensing interference portion 447a. That is, at this point in time, the surface of the sensing enclosure 459 presses against the sensing interference portion 447a to turn the sensing switch 446 into the open state. Therefore, the driving source 441 is in a state where it has stopped operating, and the rotation of the driving member 450 can also stop.

[0282] However, at the time point when the push drive 457a enters the end position 457a of the push drive 457a, which is the time point when it fully engages with the push drive 458 (the time point when it enters the end position 457a of the push drive 457a), the time point when it enters the end position 457a of the push drive 457a. Figure 32 From the state of [unclear], the maximum movement distance can be maintained during the period during which the drive member 450 further rotates by a margin angle. That is, the separation holding part 468 can further rotate a constant distance above the push holding part 458.

[0283] For example, even if the drive source 441 has in the push-holding part 458 Figure 32 The momentary stop at the position, the push-holding part 458 may also have the ability to rotate further to Figure 33 The position has a margin of clearance. Even if the drive member 450 overtravels at the instant the drive source 441 stops, causing slippage between the separation holding part 468 and the push holding part 458, the maximum travel distance of the push member 460 can be maintained. Therefore, the disengaged state of the clutch 410 can be stably maintained. If the clutch 410 disengages from the coupler 350, a washing mode with deceleration by the gear assembly 300 can be achieved.

[0284] Reference Figure 34 The diagram illustrates the state in which the driven cam 466 descends along the release drive portion 457b of the drive cam 456. Specifically, the locking drive portion 467b of the driven cam 466 descends along the inclined surface of the release drive portion 457b. This allows the driven cam 466 and the pusher 460 to descend slowly along the inclined surface of the release drive portion 457b, reducing noise and vibration generated when the pusher 460 collides with the drive member 450.

[0285] During this process, the pusher 460 descends along the axial direction toward the drive member 450. Consequently, the clutch 410 can move rearward again and switch to the engaged state with the coupler 350. The clutch 410 engaged with the coupler 350 can rotate at high speed together with the rotor 230, thereby achieving the dehydration mode.

[0286] Reference Figure 34 At the instant the pusher 460 descends completely along the axial direction, the end portion 459” of the sensing enclosure 459 overlaps with the sensing interference portion 447a, and simultaneously the sensing avoidance portion 452a reaches the sensing interference portion 447a. That is, at this point in time, the surface of the sensing enclosure 459 presses against the sensing interference portion 447a, releasing the state that opens the sensing switch 446, and the sensing switch 446 can be closed. If the sensing switch 446 is closed, the control unit recognizes the state of the pusher 460 descending completely, that is, entering the push release interval RS, and can stop the drive source 441. In this way, the rotation of the drive member 450 stops, and the state in which the pusher 460 does not push the clutch 410 can be maintained, that is, the engaged state.

[0287] At this time, with the separation holding portion 468 entering the push release interval RS formed between the two push holding portions 458, the engagement state can be maintained even if the drive member 450 rotates further by a margin angle. That is, when the drive member 450 is not precisely controlled and overtravels, the margin angle can compensate for the overtravel of the drive member 450. This is because the push release interval RS of the drive member 450 (refer to the circumferential direction of the drive member 450) is... Figure 30 This can only be achieved if the length of the AB interval is longer than the length of the separation holding portion 468 of the pusher 460 based on the circumference of the pusher 460.

[0288] As described above, in this embodiment, the control unit can be positioned at the time point when the separation holding portion 468 of the pusher 460 enters the push release interval RS of the drive member 450. Figure 34 The rotation of the drive member 450 is stopped (in the state described above). Alternatively, the control unit may stop the rotation of the drive member 450 after the drive member 450 has rotated a predetermined angle or a buffer time, starting from the point when the separation holding portion 468 of the pusher 460 enters the push release interval RS of the drive member 450. This is because, as described above, a margin angle is ensured in this embodiment to achieve this.

[0289] In summary, in this embodiment, the circumferential length of the push-release interval RS of the drive cam 456 is longer than the circumferential length of the separation holding portion 468 of the driven cam 466. If the separation holding portion 468 enters the push-release interval RS, the axial separation distance between the push member 460 and the drive member 450 becomes minimal, thereby allowing the sensing switch 446 to be turned off. As described above, if the sensing switch 446 is turned off, the control unit can control the clutch drive device 400 to stop the rotation of the drive member 450.

[0290] On the other hand, the control unit can be precisely controlled by the position of the sensing switch 446. (See reference...) Figure 32 The sensing interference portion 447a of the sensing switch 446 can be aligned radially with the starting position 467a” of the separation holding portion 468 of the pushing member 460. Simultaneously, the starting position 457a” of the pushing holding portion 458 formed in the pushing action range OS of the driving cam 456 and the starting end 459' of the sensing enclosure 459 can be aligned radially with the driving member 450. Thus, at the point when the driving member 450 rotates and the separation driving portion 467a fully engages with the pushing driving portion 457a ( Figure 32 (i) the sensing interference part 447a, (ii) the starting position 467a” of the separation holding part 468, (iii) the starting position 457a” of the push holding part 458 and (iv) the starting end 459' of the sensing enclosure 459 are aligned radially along the driving member 450.

[0291] As another example, the starting position 457a” of the push holding portion 458 formed in the push action range OS of the drive cam 456 and the starting end 459' of the sensing enclosure 459 can also be configured to have a phase difference of less than 10 degrees with respect to the center of the drive member 450. In this embodiment, there is a margin of the margin angle between the drive member 450 and the push member 460, so the starting position 457a” of the push holding portion 458 and the starting end 459' of the sensing enclosure 459 can be allowed to have a phase difference of less than 10 degrees.

[0292] In the event of an abnormal termination of the clutch drive device 400 or the roller rotation device 100, the control unit can initialize the clutch drive device 400. If the position (rotation angle) of the drive member 450 cannot be determined due to an abnormal power outage, the control unit can rotate the drive member 450 of the clutch drive device 400 one revolution. During this process, the sensing enclosure 459 can activate the sensing switch 446, and the control unit can determine the position of the drive member 450 by the opening / closing of the sensing switch 446.

[0293] As another example, instead of the sensing switch 446, a sensor such as a Hall sensor (not shown) can be provided in the clutch drive device 400. The Hall sensor measures the relative rotation angle between the drive member 450 and the push member 460, and the control unit can control the rotation of the drive member 450 based on the measured value. As yet another example, the push member 460 can also press two axially spaced switching devices (not shown) in the clutch drive device 400 when moving axially.

[0294] Figure 35 The diagram shows the drive member 450 and the pusher member 460, constituting a second embodiment of the roller rotating device 100 of the present invention, in a disassembled state. Only structures different from the foregoing embodiments are described; the drive cam 456 may be disposed on the top surface of the drive member 450, instead of its side surface (outer peripheral surface). The driven cam 466 may be disposed on the bottom surface of the pusher member 460, instead of its side surface (outer peripheral surface). (Refer to...) Figure 35 The driven cam 466 protrudes downward from the bottom surface of the pusher 460, and the driving cam 456 protrudes towards the driven cam 466 from the top surface of the drive member 450. Alternatively, one of the driving cam 456 and the driven cam 466 may be located on the side of the drive member 450 or the pusher 460.

[0295] Figure 36 The diagram shows the drive member 450 and the pusher 460 in a disassembled state according to a third embodiment of the roller rotating device 100 of the present invention. Only the structure differing from the foregoing embodiments is described; the driven cam 466 disposed on the pusher 460 can have a simple axially extending structure, rather than a structure where the axial height varies circumferentially. The driven cam 466 moves along the drive cam 456, whose axial height varies circumferentially, thereby causing the pusher 460 to rise and fall.

[0296] Figure 37The diagram shows the drive member 450 and the pusher 460 in a disassembled state according to a fourth embodiment of the roller rotating device 100 of the present invention. Only structures different from the aforementioned embodiments are described. In contrast to the third embodiment described above, the driven cam 466 disposed on the pusher 460 may have a structure in which the axial height varies circumferentially. On the other hand, the drive cam 456 may have a structure that simply extends axially, rather than a structure in which the axial height varies circumferentially. The structure in which the driven cam 466 has a circumferentially varying axial height moves along the drive cam 456, thereby causing the pusher 460 to rise and fall.

[0297] As another example, although not shown, the pusher 460 can be integrally provided with the clutch 410. As yet another example, the pusher 460 is omitted, and the driven cam 466 can be directly provided on the outer or inner circumferential surface of the clutch 410, so that the clutch 410 can also move along the drive cam 456 of the drive member 450.

[0298] The above description is merely illustrative of the technical concept of the present invention. Those skilled in the art can make various modifications and variations without departing from the essential characteristics of the present invention. Therefore, the embodiments disclosed in this invention are not intended to limit the technical concept of the present invention, but rather to illustrate that the scope of the technical concept of the present invention is not limited by these embodiments. The scope of protection of this invention should be interpreted by the appended claims, and should be interpreted as including all technical concepts within the equivalent scope of the claims.

Claims

1. A drum rotating device, wherein, include: The output shaft is connected to the roller. A motor, comprising a stator and a rotor that rotates relative to the stator; A gear assembly, including a motor shaft connected to the motor, transmits the rotational force of the rotor to the output shaft; The clutch is adjusted to move axially along the motor shaft and connect to the rotor, transmitting the speed change drive of the gear assembly to the output shaft; as well as A clutch drive mechanism that moves the clutch along the axial direction; The clutch drive device includes: The drive source provides rotational force; A drive component having a rotation center concentric with the motor shaft and rotated by the drive source; and The pusher moves along the axial direction in conjunction with the rotation of the drive member, causing the clutch to move along the axial direction.

2. The drum rotating device according to claim 1, wherein, The drive member is disposed in the clutch drive device to limit the movement of the drive member along the axial direction; The pusher is disposed in the clutch drive device to limit the relative rotation of the pusher and the drive member.

3. The drum rotating device according to claim 1, wherein, The driving component and the pushing component are configured to be concentric with each other.

4. The drum rotating device according to claim 1, wherein, The driving member and the pushing member are configured to respectively surround the motor shaft.

5. The drum rotating device according to claim 1, wherein, The drive member is configured to be closer to the motor in the axial direction than the pusher member; The drive member moves the pusher away from the motor in the axial direction.

6. The drum rotating device according to claim 1, wherein, The driving member and the pushing member are respectively configured to surround the motor shaft; The driving member and the pushing member overlap each other in the radial direction.

7. The drum rotating device according to claim 1, wherein, The clutch, the drive member, and the pusher are configured to overlap each other in the radial direction.

8. The drum rotating device according to claim 1, wherein, The driving member and the pushing member are concentric with each other and respectively surround the motor shaft; The pusher is guided by the outer peripheral surface of the drive member, thereby moving along the axial direction.

9. The drum rotating device according to claim 1, wherein, The stator and the gear assembly are spaced apart from each other along the axial direction; The clutch drive device is axially disposed between the stator and the gear assembly; The clutch drive unit is coupled to the stator and the gear assembly, respectively.

10. The drum rotating device according to claim 1, wherein, The diameter of the clutch drive device is smaller than the diameter of the gear assembly, and the diameter of the clutch drive device is smaller than the diameter of the motor.

11. The drum rotating device according to claim 1, wherein, One of the driving member and the pushing member is provided with a guide cam portion whose axial length varies circumferentially; A lifting guide portion guided by the guide cam portion is provided on the other side of the driving member and the pushing member; If the drive member rotates, the lifting guide portion moves along the guide cam portion in the axial direction.

12. The drum rotating device according to claim 1, wherein, The driving member is provided with a driving cam whose axial length varies along the circumference of the driving member; The pusher is provided with a driven cam, which is guided by the drive cam, and the axial length of the driven cam varies along the circumference of the pusher. If the driving member rotates, the driven cam moves along the driving cam in the axial direction.

13. The drum rotating device according to claim 12, wherein, The drive cam has a push drive part, which has a first tilt angle relative to the circumferential direction of the drive member; The driven cam has a separation drive section, which has an inclination angle relative to the pusher in the circumferential direction that is the same as the first inclination angle; The push drive unit and the separation drive unit are configured to face each other.

14. The drum rotating device according to claim 1, wherein, The gear assembly includes: The gear housing has an internal mounting space; and A plurality of gears are configured in the mounting space and are linked to the rotation of the motor shaft; The clutch drive unit is fixed to the gear cover in a manner that surrounds the motor shaft.

15. The drum rotating device according to claim 1, wherein, The clutch drive device includes: The drive housing has an internal operating space and is equipped with the drive source; The driving member is disposed in the action space and rotates by receiving the rotational force of the driving source; and The pusher, at least a portion of which is disposed in the action space, moves along the axial direction.

16. The drum rotating device according to claim 15, wherein, A portion of the pusher extends into and out of the action space along the axial direction.

17. The drum rotating device according to claim 15, wherein, The drive housing is provided with an anti-rotation part that interferes with the push member in the circumferential direction; The anti-rotation part is continuously formed along the moving direction of the pusher.

18. The drum rotating device according to claim 15, wherein, A radially recessed anti-rotation groove is formed in the drive housing; The pusher is provided with an anti-rotation protrusion, which protrudes radially and is inserted into the anti-rotation groove; The anti-rotation groove extends along the moving direction of the pusher.

19. The drum rotating device according to claim 15, wherein, The drive housing has an opening for the pusher to move in and out; The radius of the moving hole of the pusher is smaller than the radial distance between the center of the pusher and the end of the anti-rotation protrusion.

20. The drum rotating device according to claim 1, wherein, The drive source is configured to be radially spaced from the drive member and the push member, respectively, along the clutch drive device; The radial distance between the rotation center of the drive member and the drive source is shorter than the radial distance from the rotation center of the gear assembly to the radial end of the gear assembly; The radial distance from the rotation center of the drive member to the drive source is shorter than the radial distance from the rotation center of the motor to the edge of the motor.

21. The drum rotating device according to claim 1, wherein, The driving component includes: A ring-shaped driving body; A drive gear, disposed circumferentially on the surface of the drive body, meshes with the drive source and rotates thereon; and A drive cam is disposed on the surface of the drive body along the circumference of the drive member, and the axial distance of the drive cam varies along the circumference.

22. The drum rotating device according to claim 21, wherein, The drive gear and the drive cam are respectively disposed on different surfaces of the drive body; The radial distance from the rotation center of the drive member to the drive gear is greater than the radial distance from the rotation center of the drive member to the drive cam.

23. The drum rotating device according to claim 1, wherein, A guide wall is provided along the circumference of the driving member; A drive cam is provided on the surface of the guide wall, and the axial distance of the drive cam varies along the circumference of the guide wall; The pusher is configured to surround the guide wall; A driven cam corresponding to the driving cam is provided on the outer peripheral surface of the pusher facing the guide wall.

24. The drum rotating device according to claim 1, wherein, The pusher and the clutch are respectively formed with push surfaces and contact support portions facing each other along the axial direction; The pushing surface and the contact support remain in surface contact with each other.

25. The drum rotating device according to claim 1, wherein, An elastic member that extends and retracts along the axial direction is provided between the gear assembly and the clutch; The elastic member provides an elastic force to the clutch in the axial direction.

26. The drum rotating device according to claim 1, wherein, The driving member is provided with a driving cam that extends circumferentially along the driving member; The drive cam includes: The first cam portion has an axial length that increases or decreases circumferentially along the drive member; and The second cam portion is connected to the first cam portion and has an inclination angle relative to the circumference of the driving member that is smaller than the inclination angle of the first cam portion.

27. The drum rotating device according to claim 1, wherein, A sensing enclosure is provided along the circumference of the driving member at the edge of the driving member; A sensing avoidance portion, which omits the sensing enclosure, is formed along the circumference of the driving member at the edge of the driving member. During the rotation of the driving member, the sensing enclosure interferes with the sensing switch, causing the sensing switch to open or close. During the rotation of the driving member, the sensing avoidance part causes the sensing switch to close or open.

28. The drum rotating device according to claim 1, wherein, The driving member is provided with a driving cam that extends circumferentially along the driving member; A sensing enclosure is provided along the circumference of the driving member at the edge of the driving member; The driving component is provided with the same number of the driving cams and the sensing enclosure.

29. A drum rotating device, wherein, include: The output shaft is connected to the roller. A motor, comprising a stator and a rotor that rotates relative to the stator, and having a coupler coupled to the rotor; A gear assembly, including a motor shaft connected to the motor, transmits the rotational force of the rotor to the output shaft; The clutch is adjusted to move axially along the motor shaft and connected to the coupler to transmit the speed change drive of the gear assembly to the output shaft; as well as A clutch drive mechanism that moves the clutch along the axial direction; The clutch drive device includes: The driving component has a rotation center concentric with the motor shaft and is rotated by a driving source; as well as The pusher moves along the axial direction in conjunction with the rotation of the drive member, and overlaps with the drive member in the radial direction, causing the clutch to move along the axial direction.

30. The drum rotating device according to claim 29, wherein, The drive member is configured in the clutch drive device to rotate in a restricted state along the axial direction; The pusher and the drive member are concentrically disposed in the clutch drive device, and move along the axial direction in a rotationally restricted state.

31. The drum rotating device according to claim 29, wherein, The pushing member moves along the axial direction in conjunction with the rotation of the driving member; The pusher causes the clutch to move along the axial direction to engage with the coupler.

32. A drum rotating device, wherein, include: The output shaft is connected to the roller. as well as A motor, comprising a stator and a rotor that rotates relative to the stator; The motor includes: A gear assembly, including a motor shaft, transmits the rotational force of the rotor to the output shaft; The clutch is adjusted to move axially along the motor shaft and connect to the rotor, transmitting the speed change drive of the gear assembly to the output shaft; A drive component having a rotation center concentric with the motor shaft and rotating therearound; and The pusher moves along the axial direction in conjunction with the rotation of the drive member, causing the clutch to move along the axial direction; At least one of the surfaces of the driving member and the opposing surface of the pusher is provided with a cam portion that interferes with the other in the circumferential direction.

33. The drum rotating device according to claim 32, wherein, A drive cam with an axial length that varies circumferentially is provided on one surface of the drive member; The pusher, facing a surface of the drive member, is provided with a driven cam that is guided by the drive cam; If the driving member rotates, the driven cam moves along the driving cam in the axial direction.

34. A garment processing device, wherein, include: The drum rotating device according to any one of claims 1 to 33; as well as The roller, rotated by the roller rotating device, forms a storage space inside.

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