Direct-driven dual-power clutch and washing machine

Abstract

The utility model relates to the technical field of washing machines, and provides a direct drive type dual-power clutch and a washing machine, the direct drive type dual-power clutch comprises an impeller shaft, a dewatering shaft sleeve, a gear box, a clutch sleeve, a reset compression spring and a shifting fork mechanism, the impeller shaft penetrates through the clutch, and the lower end of the impeller shaft serves as an input end to be directly connected with a motor in a direct drive mode; and the shifting fork mechanism is matched with the reset pressure spring to switch the upper position and the lower position of the clutch sleeve, so that meshing transmission between the clutch sleeve and the input end of the impeller shaft or relative fixation between the clutch sleeve and the mounting plate is realized. According to the direct-drive type dual-power clutch, due to the direct-drive type power transmission and dual-power-source design, the transmission efficiency of the clutch is remarkably improved, energy loss is reduced, and due to the adoption of the planetary gear transmission mechanism and the matched design of the shifting fork mechanism and the reset compression spring, the transmission efficiency of the clutch is greatly improved. The stability and the reliability of the clutch in the working process are ensured, the possibility of failure occurrence is reduced, and smoother and more efficient washing and dewatering experience is provided for a user.

Description

Technical Field

[0001] The utility model relates to the technical field of washing machines, and particularly relates to a direct-drive dual-power clutch and a washing machine. Background Art

[0002] In the current technical field of washing machines, the pulsator washing machine is widely popular because of its simple structure and convenient operation. However, with the continuous improvement of consumers' demands for washing effects, energy efficiency ratios, and diversified washing modes, some limitations of traditional pulsator washing machines have gradually emerged in technology. In particular, in the design of dual-power washing machines, how to efficiently and stably achieve the synchronous or reverse rotation of the pulsator and the washing tub has become a technical problem to be solved urgently.

[0003] At present, most dual-power washing machines on the market adopt a reduction gear train or a dual-motor structure to achieve the synchronous or reverse movement of the pulsator and the washing tub. The reduction gear train has a complex structure, low transmission efficiency, and is prone to energy loss; while the dual-motor structure can achieve relatively precise synchronous or reverse control, but has a high cost, and increases the complexity and failure rate of the whole machine. In addition, some direct-drive dual-power washing machines attempt to achieve this goal by improving the clutch structure, but generally have problems such as insufficient compactness, low transmission efficiency, and poor stability. Summary of the Utility Model

[0004] In view of this, the utility model aims to provide a direct-drive dual-power clutch and a washing machine to solve at least one of the problems of low transmission efficiency, large energy loss, unstable transmission, and high failure rate in the dual-power design of pulsator washing machines in the prior art.

[0005] To achieve the above object, the technical solution of the utility model is realized as follows:

[0006] A direct-drive dual-power clutch includes:

[0007] A pulsator shaft, which penetrates through the clutch and takes its lower end as the input end;

[0008] A dehydration shaft sleeve, which is installed on the mounting plate through a large water seal and a first rolling bearing and can rotate relative to it;

[0009] A gearbox, including a brake wheel, an internal gear ring, a planet carrier, planet gears, and an input central gear. The input central gear is sleeved on the pulsator shaft. The internal gear ring is fixedly connected to the brake wheel. The planet gears are movably installed on the pins of the planet carrier. The upper end of the brake wheel is fixedly connected to the dehydration shaft sleeve. The lower end of the brake wheel is internally and concentrically and movably installed with a lower shaft sleeve through a third rolling bearing. The lower part of the planet carrier is connected to the lower shaft sleeve;

[0010] A clutch sleeve, which is sleeved on the lower shaft sleeve;

[0011] A return compression spring is arranged between the clutch sleeve and the third rolling bearing;

[0012] A fork mechanism, in cooperation with the return compression spring, switches the vertical position of the clutch sleeve to achieve meshing transmission between the clutch sleeve and the input end of the wave wheel shaft or relative fixation with the mounting plate.

[0013] Further, the clutch sleeve is sleeved on the lower shaft sleeve through a spline connection and can axially move actively. A clutch sleeve upper tooth is arranged on the upper part of the clutch sleeve, and a clutch sleeve lower tooth is arranged on the lower part of the clutch sleeve.

[0014] Further, when the fork mechanism, in cooperation with the return compression spring, switches the clutch sleeve to the upper working condition, the clutch sleeve upper tooth at the upper end of the clutch sleeve meshes and locks with the fork seat in the fork mechanism. The lower shaft sleeve and the planet carrier are fixed and immovable, and the wave wheel shaft is driven by the motor to rotate, realizing the reverse rotation of the wave wheel shaft and the dehydration shaft sleeve; when the fork mechanism, in cooperation with the return compression spring, switches the clutch sleeve to the lower working condition, the clutch sleeve lower tooth at the lower end of the clutch sleeve meshes with the movable tooth at the lower end of the wave wheel shaft. The clutch sleeve, the lower shaft sleeve and the planet carrier are meshed with the wave wheel shaft as a whole, and the wave wheel shaft is driven by the motor to rotate, and the wave wheel shaft and the dehydration shaft sleeve rotate in the same direction as a whole.

[0015] Further, the fork mechanism includes:

[0016] A fork seat, on which a fixed tooth is arranged for meshing and locking the clutch sleeve with the clutch sleeve upper tooth when the clutch sleeve is in the upper position;

[0017] A fork, which is hinged and fixed on the fork seat through a fork rotating shaft and can drive the clutch sleeve to slide up and down along the lower shaft sleeve.

[0018] Further, the fork seat is fixed on a bearing support, and the bearing support is fixedly connected concentrically with the mounting hole on the mounting plate.

[0019] Further, the lower part of the brake wheel is fixedly connected to the first lower end, and it is movably installed in the bearing support through a second rolling bearing.

[0020] Further, the upper end of the wave wheel shaft is concentrically and movably installed in the dehydration shaft sleeve through an oil-impregnated bearing, and the part of the wave wheel shaft as the input shaft in the clutch is concentrically and movably installed in the lower shaft sleeve through an oil-impregnated bearing.

[0021] Further, in the normal state, the return compression spring presses the clutch sleeve to the lower position to mesh with the movable tooth at the lower end of the wave wheel shaft.

[0022] Further, the movable tooth fixing sleeve is sleeved on the lower end of the wave wheel shaft, the lower end of the wave wheel shaft is fixedly connected to the motor rotor, the motor rotor and the motor stator are concentrically sleeved, and the motor stator can provide a rotating magnetic field for the rotation of the motor rotor.

[0023] Compared with the prior art, the direct drive dual power clutch of the present invention has the following advantages:

[0024] (1) The direct drive dual power clutch of the present invention, through the direct drive power transmission and dual power source design, significantly improves the transmission efficiency of the clutch, reduces energy loss. The adoption of the planetary gear transmission mechanism and the cooperative design of the fork mechanism and the return compression spring ensure the stability and reliability of the clutch during operation, reduce the possibility of failures, and provide users with a smoother and more efficient washing and dehydration experience.

[0025] (2) The direct drive dual power clutch of the present invention, through the direct drive dual power clutch design, adopts a planetary gear transmission mechanism, combines the dual power sources of the wave wheel shaft and the dehydration shaft sleeve, not only improves the transmission efficiency, reduces energy loss, but also ensures the smoothness and reliability of power transmission, realizes efficient power switching in the dual modes of washing and dehydration. At the same time, the concentric fixed connection between components further improves the transmission accuracy and efficiency, reduces the failure rate, and provides users with a quieter and more stable laundry environment.

[0026] Another object of the present invention is to propose a washing machine provided with the direct drive dual power clutch as described above.

[0027] The washing machine has the same advantages as the above direct drive dual power clutch compared with the prior art, and will not be elaborated here. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The accompanying drawings forming a part of the present invention are used to provide a further understanding of the present invention. The schematic embodiments and descriptions thereof of the present invention are used to explain the present invention and do not constitute an improper limitation to the present invention. In the drawings:

[0029] Figure 1 is a schematic diagram of the working principle of the direct drive dual power clutch according to an embodiment of the present invention;

[0030] Figure 2 is a front view structural schematic diagram of the direct drive dual power clutch according to an embodiment of the present invention;

[0031] Figure 3 is a top view structural schematic diagram of the direct drive dual power clutch according to an embodiment of the present invention;

[0032] Figure 4Schematic diagram of the first sectional view of the direct-drive dual-power clutch according to the embodiment of the present utility model;

[0033] Figure 5 Schematic diagram of the second sectional view of the direct-drive dual-power clutch according to the embodiment of the present utility model;

[0034] Explanation of reference numerals:

[0035] 1. Washboard shaft; 2. Dehydration shaft sleeve; 3. Large water seal; 4. First rolling bearing; 5. Mounting plate; 6. Brake wheel; 7. Planet carrier; 8. Planet gear; 9. Internal gear ring; 10. Bearing support; 11. Lower shaft sleeve; 12. First lower end; 13. Motor stator; 14. Motor rotor; 15. Clutch sleeve upper teeth; 16. Clutch sleeve; 17. Clutch sleeve lower teeth; 18. Movable teeth; 19. Return compression spring; 20. Fixed teeth; 21. Fork seat; 22. Fork rotating shaft; 23. Fork; 24. Second rolling bearing; 25. Third rolling bearing; 26. Input center gear; 27. Oil-impregnated bearing; 28. Mounting hole. Detailed implementation manners

[0036] In order to make the technical means, objectives and effects of the present utility model easy to understand, the embodiments of the present utility model will be described in detail below with reference to specific drawings.

[0037] It should be noted that all the terms for indicating directions and positions in the present utility model, such as: "upper", "lower", "left", "right", "front", "rear", "vertical", "horizontal", "inner", "outer", "top", "bottom", "lateral", "longitudinal", "center", etc., are only used to explain the relative positional relationship and connection situation between components in a specific state (as shown in the drawings), and are only for the convenience of describing the present utility model, rather than requiring the present utility model to be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present utility model. In addition, the descriptions involving "first", "second", etc. in the present utility model are only for descriptive purposes, and cannot be construed as indicating or implying their relative importance or implicitly indicating the quantity of the indicated technical features.

[0038] In the description of the present utility model, unless otherwise clearly specified and limited, the terms "installation", "connection", and "connection" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection; it can be directly connected, or indirectly connected through an intermediate medium, and it can be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific situations.

[0039] In the description of this specification, the description with reference to terms such as "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present utility model. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0040] As Figures 1 to 5 shown, this application discloses a direct-drive dual-power clutch, including:

[0041] A pulsator shaft 1, which penetrates through the clutch and takes its lower end as the clutch input end;

[0042] A dehydration shaft sleeve 2, which is installed on a mounting plate 5 through a large water seal 3 and a first rolling bearing 4 and can rotate freely relative thereto;

[0043] A gearbox, including a brake wheel 6, an internal gear ring 9, a planet carrier 7, planet gears 8, and an input central gear 26. The input central gear 26 is sleeved on the pulsator shaft 1. The internal gear ring 9 is fixedly connected to the brake wheel 6. The planet gears 8 are movably installed on the pins of the planet carrier 7. The upper end of the brake wheel 6 is fixedly connected to the dehydration shaft sleeve 2. A lower shaft sleeve 11 is concentrically and movably installed inside the first lower end 12 of the brake wheel 6 through a third rolling bearing 25. The lower part of the planet carrier 7 is connected to the lower shaft sleeve 11;

[0044] A clutch sleeve 16, which is sleeved on the lower shaft sleeve 11;

[0045] A return compression spring 19, which is arranged between the clutch sleeve 16 and the third rolling bearing 25;

[0046] A fork mechanism, which cooperates with the return compression spring 19 to switch the up and down positions of the clutch sleeve 16, so as to realize the meshing transmission between the clutch sleeve 16 and the input end of the pulsator shaft 1 or the relative fixation with the mounting plate 5.

[0047] The direct-drive dual-power clutch disclosed in this application passes the pulsator shaft 1 of the clutch through the entire clutch, and uses its lower end as the input end of the clutch. A planetary gear transmission mechanism (including a planet carrier 7, planetary gears 8, an input central gear 26, an internal gear ring 9, and a brake wheel 6) is used as the gear transmission structure for power transmission, and the pulsator shaft 1 and the dewatering shaft sleeve 2, two power output sources, are integrated to achieve power switching of the washing machine in two working modes of washing and dewatering. Through the ingenious cooperation of the fork mechanism and the return compression spring 19, the meshing transmission between the clutch sleeve 16 and the input end of the pulsator shaft 1 or the clutch switching of relative fixation with the mounting plate 5 is realized, enabling the washing machine to flexibly select the power output path according to different working modes.

[0048] For the direct-drive dual-power clutch described in this application, through direct-drive power transmission and dual-power source design, the transmission efficiency of the clutch is significantly improved, energy loss is reduced. The adoption of the planetary gear transmission mechanism and the cooperative design of the fork mechanism and the return compression spring ensure the stability and reliability of the clutch during operation, reduce the possibility of faults, and provide users with a smoother and more efficient washing and dewatering experience.

[0049] As a preferred example of this application, the clutch sleeve 16 is sleeved on the lower shaft sleeve 11 through a spline connection and can axially move. A clutch sleeve upper tooth 15 is provided on its upper part, and a clutch sleeve lower tooth 17 is provided on its lower part. In the example of this application, an external spline groove is set at the lower part of the lower shaft sleeve 11, and an internal spline groove is also provided inside the clutch sleeve 16, which can cooperate with the external spline groove of the lower shaft sleeve 11 and axially move. When the fork mechanism cooperates with the return compression spring 19 to switch the clutch sleeve 16 to the upper position condition, the clutch sleeve upper tooth 15 at the upper end of the clutch sleeve 16 meshes and fixes with the fork seat 21 in the fork mechanism, realizing the locking of the clutch sleeve 16. Further, the lower shaft sleeve 11 and the planet carrier 7 are fixed, and through the gear transmission structure inside the gearbox, when the pulsator shaft 1 is driven by the motor to rotate, the reverse rotation of the pulsator shaft 1 and the dewatering shaft sleeve 2 is realized; when the fork mechanism cooperates with the return compression spring 19 to switch the clutch sleeve 16 to the lower position condition, the clutch sleeve lower tooth 17 at the lower end of the clutch sleeve 16 meshes with the movable tooth 18 at the lower end of the pulsator shaft 1, and the clutch sleeve 16, the lower shaft sleeve 11, and the planet carrier 7 are meshed with the pulsator shaft 1 as a whole, and the rotating part of the entire clutch becomes a whole. When the pulsator shaft 1 is driven by the motor to rotate, the pulsator shaft 1 and the dewatering shaft sleeve 2 rotate in the same direction as a whole.

[0050] This setting discloses a switching method of the clutch sleeve 16. Through the spline connection between the clutch sleeve 16 and the lower shaft sleeve 11 and the design of the upper and lower teeth, the rapid switching between the washing state and the dewatering state of the washing machine can be realized, and the stability and reliability of the transmission system can be ensured.

[0051] As a preferred example of the present application, the fork mechanism includes:

[0052] A fork seat 21, on which a fixed tooth 20 is provided for engaging and locking the clutch sleeve 16 with the upper teeth 15 on the clutch sleeve when the clutch sleeve 16 is in the upper position;

[0053] A fork 23, which is hinged and fixed to the fork seat 21 through a fork rotating shaft 22 and can drive the clutch sleeve 16 to slide up and down along the lower shaft sleeve 11.

[0054] This setting discloses the specific structure of a fork device, realizing the rapid switching of the upper and lower working positions of the clutch sleeve 16, and at the same time ensuring the fixation or rotation of the brake wheel 6 in different states. The structure is compact and the assembly is convenient.

[0055] As a preferred example of the present application, the fork seat 21 is fixed on the bearing bracket 10, and the bearing bracket 10 is fixedly and concentrically connected to the mounting hole 28 on the mounting plate 5. In the example of the present application, the dehydration shaft sleeve 2 is installed in the mounting hole 28 through a large water seal 3 and a first rolling bearing 4 and can be driven to rotate by the brake wheel 6. This setting, on the one hand, ensures the concentricity of the lower shaft sleeve 11, the clutch sleeve 16, and the wave wheel shaft 1 during the working process, reducing vibration, noise, and wear caused by shaft misalignment, thereby improving the stability and service life of the entire transmission system. On the other hand, it helps to ensure the correct meshing between gears, thereby improving the transmission accuracy and efficiency, reducing the failure rate of the transmission system, simplifying the installation and debugging process, and saving installation time and debugging costs.

[0056] As a preferred example of the present application, the lower part of the brake wheel 6 is fixedly connected to a first lower end 12, and it is movably installed in the bearing bracket 10 through a second rolling bearing 24. This setting realizes the flexible operation of the brake wheel 6 and further enhances the stability and reliability of the transmission system.

[0057] As a preferred example of the present application, the upper end of the wave wheel shaft 1 is concentrically and movably installed in the dehydration shaft sleeve 2 through an oil-impregnated bearing 27, and the part of the wave wheel shaft 1 as the input shaft in the clutch is concentrically and movably installed in the lower shaft sleeve 11 through an oil-impregnated bearing 27. The design not only ensures the high concentricity of the wave wheel shaft 1 during operation, reduces vibration and wear caused by misalignment, thereby extending the service life of the components, but also improves the smoothness and efficiency of the overall transmission.

[0058] As a preferred example of the present application, the reset compression spring 19 presses the clutch sleeve 16 downward in the normal state to engage with the movable tooth 18 at the lower end of the agitator shaft 1. This design enables the clutch sleeve 16 to move upward against the action of the reset compression spring 19 during the washing state of the washing machine, thereby ensuring the stability of the engagement between the clutch sleeve 16 and the fixed tooth 20 relative to the mounting plate 5. After the washing is completed, the fork 23 resets, and the clutch sleeve 16 automatically returns to the lower position to engage with the movable tooth 18 under the action of the reset compression spring 19, simplifying the operation process and ensuring the stability and reliability of the transmission system of the washing machine in different working states, thus improving the working efficiency and durability of the washing machine.

[0059] As a preferred example of the present application, the clutch sleeve 16 can also be in the upper position and engaged with the fixed tooth 20 under the action of the reset compression spring 19 or other torsion springs (provided at the fork rotating shaft) or suspension springs in the normal state, so that the dual-power clutch described in the present application is in the washing working condition during supply or in the normal state.

[0060] As a preferred example of the present application, the movable tooth 18 is fixedly sleeved on the lower end of the agitator shaft 1 (i.e., the input end of the clutch), the lower end of the agitator shaft 1 is fixedly connected to the motor rotor 14, the motor rotor 14 and the motor stator 13 are concentrically sleeved, and the motor stator 13 can provide a rotating magnetic field for the rotation of the motor rotor 14. As a preferred example of the present application, the motor stator 13 is fixedly installed on the bearing support 10.

[0061] This setting makes the direct-drive dual-power clutch described in the present application further improve the reliability and accuracy of the transmission. It not only optimizes the power transmission path and improves the transmission efficiency, but also brings a more stable and efficient washing and dehydration experience to users by enhancing the structural stability and concentricity.

[0062] As a preferred example of the present application, the input central gear 26 meshes and drives with the planetary gear 8, and the planetary gear 8 meshes and drives with the internal gear ring 9.

[0063] This setting discloses a transmission method of the internal gear ring 9, the planetary gear 8 and the input central gear 26 inside the gearbox.

[0064] Under the washing condition, when the fork 23 is rotated by a certain angle under the action of external force, the clutch sleeve 16 is moved up along the lower sleeve 11 to the upper part, and the teeth 15 on the clutch sleeve are meshed with the fixed teeth 20, locking the clutch sleeve 16, and then the lower sleeve 11 and the planetary carrier 7 are fixed. When the input shaft (pulsator shaft 1) of the clutch rotates, the input center gear 26 drives the planetary gear 8 to rotate, and then drives the inner gear ring 9 to rotate. According to the working principle of the planetary gear system, the inner gear ring 9 rotates in the opposite direction with a reduced speed relative to the input center gear 26. The pulsator shaft 1 drives the pulsator to rotate, and at the same time, the inner gear ring 9 drives the dehydration sleeve 2 to rotate in the opposite direction with a reduced speed. The dehydration sleeve 2 is connected to the washing tub of the washing machine, realizing the reverse rotation of the pulsator and the washing tub. The rotation speed of the washing tub is lower than the rotation speed of the pulsator, and the effect of a dual-power washing machine is obtained.

[0065] Under the dehydration condition, the shift fork 23 rotates in the opposite direction by a certain angle under the action of external force and disengages from the clutch sleeve 16. Under the action of the reset compression spring 19, the clutch sleeve 16 moves a certain distance axially along the lower sleeve 11 and is in the lower position. The lower teeth 17 of the clutch sleeve are engaged with the movable teeth 18, so that the clutch sleeve 16 engages with the lower sleeve 11 and rotates together. Therefore, the lower sleeve 11 and the planetary carrier 7 rotate together with the input center gear 26. According to the working principle of the planetary gear train, the inner ring 9 also rotates together. Therefore, the rotating part of the clutch becomes a whole, and the impeller shaft and the dehydration sleeve rotate synchronously, so that the impeller and the washing tub rotate synchronously and the dehydration effect is achieved.

[0066] The present application also discloses a washing machine, on which is arranged a direct-drive dual-power clutch as described in the above embodiment.

[0067] The direct-drive dual-power clutch and washing machine described in the present application, through the direct-drive dual-power clutch design, adopts a planetary gear transmission mechanism, combined with the dual power source of the impeller shaft and the dehydration shaft sleeve, which not only improves the transmission efficiency and reduces energy loss, but also ensures the smoothness and reliability of power transmission, and realizes efficient power switching in the dual modes of washing and dehydration. At the same time, the concentric fixed connection between the components further improves the transmission accuracy and efficiency, reduces the failure rate, and provides users with a quieter and more stable laundry environment.

[0068] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A direct-drive dual-power clutch, characterized in that: include: The pulsator shaft (1) passes through the clutch and its lower end serves as an input end; The dehydration sleeve (2) is mounted on the mounting plate (5) via a large water seal (3) and a first rolling bearing (4) and is capable of rotating relative thereto; A gearbox, comprising a brake wheel (6), an inner gear ring (9), a planet carrier (7), a planetary gear (8), and an input central gear (26), wherein the input central gear (26) is sleeved on a pulsator shaft (1), the inner gear ring (9) is fixedly connected to the brake wheel (6), the planetary gear (8) is movably mounted on a pin of the planet carrier (7), the upper end of the brake wheel (6) is fixedly connected to the dewatering sleeve (2), a lower sleeve (11) is movably mounted concentrically inside the first lower end (12) of the brake wheel (6) via a third rolling bearing (25), and the lower part of the planet carrier (7) is connected to the lower sleeve (11); A clutch sleeve (16) sleeved on the lower shaft sleeve (11); A return compression spring (19) is arranged between the clutch sleeve (16) and the third rolling bearing (25); The shift fork mechanism cooperates with the return compression spring (19) to switch the clutch sleeve (16) to an upper and lower position, thereby realizing meshing transmission between the clutch sleeve (16) and the input end of the impeller shaft (1) or relative fixation with the mounting plate (5).

2. The direct-drive dual power clutch according to claim 1, characterized in that: The clutch sleeve (16) is mounted on the lower shaft sleeve (11) via a spline connection sleeve and is capable of active axial movement. Clutch sleeve upper teeth (15) are arranged on the upper part of the clutch sleeve (16), and clutch sleeve lower teeth (17) are arranged on the lower part of the clutch sleeve (16).

3. The direct-drive dual power clutch according to claim 2, characterized in that: When the shift fork mechanism cooperates with the reset compression spring (19) to switch the clutch sleeve (16) to the upper working condition, the clutch sleeve upper teeth (15) at the upper end of the clutch sleeve (16) are meshed and fixed with the shift fork seat (21) in the shift fork mechanism, the lower shaft sleeve (11) and the planetary carrier (7) are fixed, and the impeller shaft (1) is driven by the motor to rotate, thereby realizing the reverse rotation of the impeller shaft (1) and the dehydration shaft sleeve (2); when the shift fork mechanism cooperates with the reset compression spring (19) to switch the clutch sleeve (16) to the lower working condition, the clutch sleeve lower teeth (17) at the lower end of the clutch sleeve (16) are meshed with the movable teeth (18) at the lower end of the impeller shaft (1), the clutch sleeve (16), the lower shaft sleeve (11) and the planetary carrier (7) are meshed with the impeller shaft (1) as a whole, the impeller shaft (1) is driven by the motor to rotate, and the impeller shaft (1) and the dehydration shaft sleeve (2) rotate in the same direction as a whole.

4. The direct-drive dual power clutch according to claim 2 or 3, characterized in that: The fork mechanism comprises: A shift fork seat (21), on which a fixed tooth (20) is arranged, for engaging with teeth (15) on the clutch sleeve to lock the clutch sleeve (16) when the clutch sleeve (16) is in an upper position; The shift fork (23) is hingedly fixed on the shift fork seat (21) via a shift fork rotating shaft (22), and can drive the clutch sleeve (16) to slide up and down along the lower shaft sleeve (11).

5. The direct-drive dual power clutch according to claim 4, characterized in that: The fork seat (21) is fixed on the bearing support (10), and the bearing support (10) is coaxially fixedly connected to the mounting hole (28) on the mounting plate (5).

6. The direct-drive dual power clutch according to claim 5, characterized in that: The lower part of the brake wheel (6) is fixedly connected to the first lower end (12), and is movably mounted in the bearing support (10) via a second rolling bearing (24).

7. The direct-drive dual power clutch according to claim 1, characterized in that: The upper end of the impeller shaft (1) is coaxially mounted in the dehydration sleeve (2) via an oil-containing bearing (27), and the part of the impeller shaft (1) serving as the input shaft in the clutch is coaxially mounted in the lower sleeve (11) via an oil-containing bearing (27).

8. The direct-drive dual power clutch according to claim 1, characterized in that: The return compression spring (19) presses the clutch sleeve (16) to a lower position under normal conditions so as to mesh with the movable teeth (18) at the lower end of the impeller shaft (1).

9. The direct-drive dual power clutch according to claim 8, characterized in that: The movable teeth (18) are fixedly sleeved on the lower end of the impeller shaft (1); the lower end of the impeller shaft (1) is fixedly connected to the motor rotor (14); the motor rotor (14) and the motor stator (13) are concentrically sleeved; and the motor stator (13) can provide a rotating magnetic field for the rotation of the motor rotor (14).

10. A washing machine, characterized in that: A direct-drive dual-power clutch as claimed in any one of claims 1 to 9 is arranged on the washing machine.

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