Novel dual-drive washing machine clutch

Abstract

The utility model discloses a novel dual-drive washing machine clutch. The clutch comprises an input gear shaft, a flange clutch shaft sleeve, an output inner shaft, an output shaft sleeve, a first planetary gear transmission mechanism, a transition gear and a second planetary gear transmission mechanism. A first gear is arranged at the tail end of the input gear shaft; the flange clutch shaft sleeve is sleeved on the input gear shaft; the front end of the output inner shaft is close to and spaced from the first gear; the output shaft sleeve is sleeved on the output inner shaft; the transition gear is meshed with the first planetary gear transmission mechanism and the second planetary gear transmission mechanism. According to the clutch, two working modes can be obtained when the flange clutch shaft sleeve and the driving device are switched between power connection and power disconnection. In one working mode, the input gear shaft and the output shaft sleeve output at high speed in the same direction, and in the other working mode, the input gear shaft and the output shaft sleeve output at low speed and have different rotating speeds. The clutch is simple in structure, stable and reliable in operation and high in compactness.

Description

Technical Field

[0001] The utility model relates to the technical field of washing machine accessories, in particular to a novel double-drive washing machine clutch. Background Art

[0002] The core component of a dual-drive washing machine is the dual-drive clutch, which drives the inner drum and the impeller of the washing machine to rotate in opposite directions. Traditional dual-drive clutches may have energy loss during the transmission process, resulting in low transmission efficiency. The new clutch optimizes the design of the planetary gear transmission mechanism to make the meshing between gears tighter and more precise, reducing energy loss during the transmission process and thus improving transmission efficiency. Some traditional dual-drive clutches may have insufficient structural strength when subjected to high loads or long-term operation, resulting in performance degradation or damage.

[0003] Therefore, there is room for improvement in the dual-drive washing machine clutch. Utility Model Content

[0004] The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, the utility model proposes a novel dual-drive washing machine clutch, which can achieve a significant reduction in speed and torque increase, and can improve the stability of the axis at the center of the clutch.

[0005] According to the new dual-drive washing machine clutch of the embodiment of the utility model, it includes an input gear shaft, a flange clutch sleeve, an output inner shaft, an output sleeve, a first planetary gear transmission mechanism, a transition gear and a second planetary gear transmission mechanism. The input gear shaft is arranged along the axis of the new dual-drive washing machine clutch, and the tail end of the input gear shaft is provided with a first gear; the flange clutch sleeve is sleeved on the input gear shaft; the output inner shaft is arranged along the axis, and the front end of the output inner shaft is adjacent to and spaced from the first gear; the output shaft sleeve is sleeved on the output inner shaft; the first planetary gear transmission mechanism includes: a first gear ring, a first planet carrier and at least two first planetary wheels, the first gear ring and the first planet carrier are arranged around the axis, all the first planetary wheels are rotatably connected to the first planet carrier, all the first planetary wheels surround and mesh with the first gear, and all the first The planetary gears are all meshed with the first ring gear, and the first ring gear or the first planet carrier is connected to the flange clutch sleeve; the transition gear is connected to the front end of the output inner shaft and the first planet carrier; the second planetary gear transmission mechanism includes: a second ring gear, a second planet carrier and at least two second planetary gears, the second ring gear and the second planet carrier are arranged around the axis, all the second planetary gears are rotatably connected to the second planet carrier, all the second planetary gears surround and mesh with the transition gear, all the second planetary gears are meshed with the second ring gear, the second planet carrier is connected to the first ring gear, and the second ring gear is connected to the front end of the output sleeve.

[0006] According to the clutch of the new dual-drive washing machine of the embodiment of the utility model, by setting the above-mentioned first planetary gear transmission mechanism and the second planetary gear transmission mechanism, two working modes can be obtained when the flange clutch sleeve is switched to be connected to the power of the driving device and disconnected from the power connection. In one working mode, the input gear shaft and the output sleeve output at high speed in the same direction, and in another working mode, the input gear shaft and the output sleeve both output at low speed, and the rotation speeds of the two are different. The clutch of the present application has a simple structure, stable and reliable operation, high compactness, and can meet the needs of different working modes of the new dual-drive washing machine. The setting of the two planetary gear transmission mechanisms enables the input gear shaft and the output sleeve to reduce speed with different speed reduction amplitudes, and can also achieve two speed reduction and torque increase. The single speed reduction ratio does not need to be set too high, which is conducive to reducing operating impact.

[0007] According to the new dual-drive washing machine clutch in some embodiments of the utility model, the transition gear outer sleeve rotates synchronously with the front end of the output inner shaft, and the first planetary carrier outer sleeve rotates synchronously with the transition gear.

[0008] According to some embodiments of the new dual-drive washing machine clutch, the front end of the output inner shaft forms a second gear, the inner circumferential surface of the transition gear forms transition internal teeth, the transition internal teeth are sleeved on the second gear and have an equal number of teeth; the outer circumferential surface of the transition gear forms transition external teeth, and the second planetary gear is meshed with the transition external teeth; the inner circumferential surface of the first planetary carrier forms first planetary connecting teeth, the first planetary connecting gear is sleeved on the transition external teeth and have an equal number of teeth.

[0009] According to some embodiments of the new dual-drive washing machine clutch, the first planetary frame includes: a first front frame and a first tail frame distributed along the axial direction, the first front frame and the first tail frame are both annular shapes arranged around the axis, the first planetary gear transmission mechanism also includes a first gear shaft passing through the first planetary wheel, the two ends of the first gear shaft are respectively connected to the first front frame and the first tail frame, and the first tail frame is connected to the transition gear; the second planetary frame includes: a second front frame and a second tail frame distributed along the axial direction, the second front frame and the second tail frame are both annular shapes arranged around the axis, the second planetary gear transmission mechanism also includes a second gear shaft passing through the second planetary wheel, the two ends of the second gear shaft are respectively connected to the second front frame and the second tail frame, and the second front frame is connected to the first gear ring.

[0010] In some embodiments, a first support column is integrally formed on one of the first front frame and the first tail frame, and the first support column is connected to the other of the first front frame and the first tail frame via a first fastener; a second support column is integrally formed on one of the second front frame and the second tail frame, and the second support column is connected to the other of the second front frame and the second tail frame via a second fastener.

[0011] In some embodiments, surfaces of the first front frame and the first tail frame facing each other are provided with first positioning rings in a one-to-one correspondence, and the two ends of the first gear shaft are inserted into the two first positioning rings; surfaces of the second front frame and the second tail frame facing each other are provided with second positioning rings in a one-to-one correspondence, and the two ends of the second gear shaft are inserted into the two second positioning rings.

[0012] In some optional embodiments, a retaining groove is provided on the outer circumferential surface of the second front frame, and the retaining groove is multiple and distributed at intervals along the circumferential direction; a retaining tooth is provided at the tail end of the first gear ring, and the retaining tooth is multiple and distributed at intervals along the circumferential direction, and the multiple retaining teeth are respectively retained in the multiple retaining grooves.

[0013] In some embodiments, at least one of the first planet carrier and the second planet carrier is provided with a weight-reducing hole.

[0014] In some embodiments, a mating block is provided at the front end of the first gear ring. The mating blocks are multiple and arranged at intervals along the circumferential direction, and a mating opening is formed on the front side of each mating block.

[0015] According to some embodiments of the novel dual-drive washing machine clutch, the second gear ring includes a large gear ring, a small gear ring and a connecting ring plate. The large gear ring surrounds and meshes with the second planetary gear; the small gear ring surrounds the front end of the output shaft sleeve; the connecting ring plate is arranged along the rear end of the large gear ring and connected to the outer circumference of the small gear ring; wherein the front end of the output shaft sleeve is formed with a third gear, and the small gear ring is sleeved on the third gear and has the same number of teeth.

[0016] Additional aspects and advantages of the present invention will be given in part in the following description, and in part will become apparent from the following description, or will be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0018] Figure 1 is a schematic diagram of the structure of a clutch in some embodiments of the present application;

[0019] Figure 2 yes Figure 1 Sectional view of AA in the middle;

[0020] Figure 3 is a cross-sectional view of some clutches in this application;

[0021] Figure 4 It is a partial enlarged view of B in this application;

[0022] Figure 5 is another cross-sectional view of a clutch in some embodiments of the present application;

[0023] Figure 6 is a structural schematic diagram of a first planetary gear transmission mechanism according to some embodiments of the present application;

[0024] Figure 7 is a schematic structural diagram of a first gear ring according to some embodiments of the present application;

[0025] Figure 8 It is a schematic structural diagram of the second gear ring in some embodiments of the present application.

[0026] Reference numerals:

[0027] Clutch 100, axis L,

[0028] Input gear shaft 1, first gear 11, flange clutch sleeve 2, output inner shaft 3, second gear 31,

[0029] Output shaft sleeve 4, third gear 41,

[0030] The first planetary gear transmission mechanism 5, the first gear ring 51, the matching block 513, the matching port 5131, the latching tooth 514, the first planetary frame 52, the first planetary connecting tooth 521, the first front frame 522, the first tail frame 523, the first support column 524, the first positioning ring 525, the first gear shaft 53,

[0031] Transition gear 6, transition inner gear 61, transition outer gear 62,

[0032] The second planetary gear transmission mechanism 7, the second ring gear 71, the large ring gear 711, the small ring gear 712, the connecting ring plate 713, the second planetary frame 72, the second front frame 721, the second support column 7211, the slot 7212, the second tail frame 723, the second positioning ring 724, the second gear shaft 73,

[0033] Pulley 81 and clutch sleeve 82. DETAILED DESCRIPTION

[0034] The embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0035] In the description of the present utility model, it should be understood that the terms "upper", "lower", "front", "rear", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present utility model. In addition, features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present utility model, unless otherwise specified, "multiple" means two or more.

[0036] In the description of the present invention, it should be noted that, 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 or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0037] Reference below Figure 1-Figure 8 , describing the clutch 100 of the new dual-drive washing machine according to an embodiment of the present utility model.

[0038] like Figure 1-Figure 2 As shown, the clutch 100 according to the embodiment of the present utility model includes an input gear shaft 1, a flange clutch sleeve 2, an output inner shaft 3, an output sleeve 4, a first planetary gear transmission mechanism 5, a transition gear 6 and a second planetary gear transmission mechanism 7.

[0039] like Figure 2-Figure 3 As shown, the input gear shaft 1 is arranged along the axis L of the clutch 100. It can also be said that the axis of the input gear shaft 1 is the axis L of the clutch 100, and most of the parts in the clutch 100 are extended along the axis L. A first gear 11 is provided at the rear end of the input gear shaft 1, and a flange clutch sleeve 2 is sleeved on the input gear shaft 1.

[0040] The input gear shaft 1 and the flange clutch sleeve 2 are located at the power input side of the entire clutch 100. The input gear shaft 1 is sleeved in the flange clutch sleeve 2, and the front end of the input gear shaft 1 extends out of the front end of the flange clutch sleeve 2. The front end of the input gear shaft 1 is used to connect to the drive device, and the front end of the flange clutch sleeve 2 can be switched between power connection with the drive device and power disconnection.

[0041] As is well known in the art, a clutch mechanism (not shown) cooperating with the flange clutch sleeve 2 is usually provided in the washing machine, and the clutch mechanism is used to control the connection and disconnection of the power connection between the flange clutch sleeve 2 and the driving device. Figure 2 and Figure 3As shown, the front end of the input gear shaft 1 can be covered with a clutch sleeve 82, and a pulley 81 is installed at the junction of the clutch sleeve 82 and the input gear shaft 1. The driving device directly drives the pulley 81 to rotate, and a clutch spring (not shown) is sleeved at the junction of the clutch sleeve 82 and the flange clutch sleeve 2. Under the control of the clutch mechanism, the clutch spring can switch between a relaxed state and a tightened state. When the clutch spring is in a relaxed state, the clutch sleeve 82 and the flange clutch sleeve 2 are not tightened, and the clutch sleeve 82 and the input gear shaft 1 are driven by the pulley 81 to rotate, and the input gear shaft 1 transmits power to the output side. When the clutch spring is in a tightened state, the clutch spring holds the clutch sleeve 82 and the flange clutch sleeve 2, and when the pulley 81 rotates, it drives the input gear shaft and the flange clutch sleeve 2 to rotate, that is, the input gear shaft 1 and the flange clutch sleeve 2 rotate at the same speed and in the same direction, and the input gear shaft 1 and the flange clutch sleeve 2 transmit power to the output side. Finally, the clutch 100 obtains two output operation modes, and the washing machine obtains a washing mode and a dehydration mode. Of course, the clutch mechanism does not belong to the protection scope of this application, and the switching mode of the power connection and disconnection between the flange clutch sleeve 2 and the driving device in this application can also be realized by other clutch mechanisms disclosed in the prior art.

[0042] In order to simplify the following description, it is said that the clutch 100 obtains one working mode when the flange clutch sleeve 2 is connected to the driving device in power, and obtains another working mode when the clutch 100 is disconnected from the power.

[0043] Reference Figure 2-Figure 4 The output inner shaft 3 is arranged along the axis L, and its front end is close to and spaced from the first gear 11. This arrangement can avoid direct friction and ensure that power can be transmitted smoothly.

[0044] The output shaft sleeve 4 is sleeved on the output inner shaft 3, and can be used to support and fix the output inner shaft 3. The output inner shaft 3 and the output shaft sleeve 4 are both output side components of the clutch 100, and are used to connect different components of the washing machine. Specifically, the output inner shaft 3 is used to connect the pulsator of the washing machine, and the output shaft sleeve 4 is used to connect the inner barrel of the washing machine. Of course, when the structure of the washing machine changes, the structure to be connected between the output inner shaft 3 and the output shaft sleeve 4 can also change.

[0045] like Figure 2-Figure 4 As shown, in the clutch 100 , the power transmission parts between the input side and the output side include a first planetary gear transmission mechanism 5 , a transition gear 6 and a second planetary gear transmission mechanism 7 .

[0046] like Figure 3-Figure 4 As shown, the first planetary gear transmission mechanism 5 includes a first ring gear 51, a first planet carrier 52 and at least two first planetary gears (not shown).

[0047] The first gear ring 51 and the first planet carrier 52 are arranged around the axis L, and all the first planetary gears are rotatably connected to the first planet carrier 52, that is, all the first planetary gears can rotate under the input side power drive, but when the first planetary gears rotate, their axes remain unchanged on the first planet carrier 52. The first planetary gears are meshed with the first gear ring 51, and the first gear ring 51 or the first planet carrier 52 is connected to the flange clutch sleeve 2, that is, there are two embodiments of the connection position of the flange clutch sleeve 2 in the present application, one is that the flange clutch sleeve 2 is connected to the first gear ring 51 and rotates at the same speed and in the same direction, and the other is that the flange clutch sleeve 2 is connected to the first planet carrier 52 and rotates at the same speed and in the same direction.

[0048] The arrangement of the first planetary gear transmission mechanism 5, on the one hand, utilizes the characteristics of the first planetary gear transmission mechanism 5 being in uniform power connection with the output inner shaft 3 and the output shaft sleeve 4, and the first planetary gear transmission mechanism 5 has different movement modes in the two working states of the flange clutch shaft sleeve 2 being in power connection with the drive device and being out of power connection. On the other hand, the structural characteristics of the planetary gear transmission mechanism itself can be utilized to realize the first deceleration and torque increase of the clutch 100, and the speed decreases when transmitting to the output side.

[0049] Specifically, taking the flange clutch sleeve 2 and the first gear ring 51 connected and rotating at the same speed and in the same direction as an example, when the flange clutch sleeve 2 is connected to the driving device by power, the first gear ring 51 and the first gear 11 of the input gear shaft 1 rotate at the same speed and in the same direction, and the first planetary gear has no power to rotate by itself. The movement mode of the first planetary gear transmission mechanism 5 is that the first gear ring 51, the first planetary carrier 52 and the input gear shaft 1 rotate at the same speed and in the same direction, and all the first planetary gears only revolve around the axis L of the clutch 100, and do not rotate by themselves. When the flange clutch sleeve 2 is disconnected from the driving device by power, the first gear 11 of the input gear shaft 1 rotates to drive the first planetary gear meshing therewith to rotate, thereby driving the first gear ring 51 and the first planetary carrier 52 to rotate, and the speed relative to the input gear shaft 1 decreases.

[0050] Taking the example that the flange clutch sleeve 2 is connected to the first planetary carrier 52 and rotates at the same speed and in the same direction, when the flange clutch sleeve 2 is connected to the driving device, the first planetary carrier 52 rotates at the same speed and in the same direction as the first gear 11 of the input gear shaft 1, and the first planetary gear has no power to rotate. The movement mode of the first planetary gear transmission mechanism 5 is that the first ring gear 51, the first planetary carrier 52 and the input gear shaft 1 rotate at the same speed and in the same direction, and all the first planetary gears only revolve around the axis L of the clutch 100, and do not rotate. When the flange clutch sleeve 2 is disconnected from the driving device, the first gear 11 of the input gear shaft 1 rotates to drive the first planetary gear meshing therewith to rotate, thereby driving the first ring gear 51 and the first planetary carrier 52 to rotate, and the speed relative to the input gear shaft 1 decreases.

[0051] like Figure 3-Figure 5As shown, the transition gear 6 is connected to the front end of the output inner shaft 3 and the first planetary carrier 52 . The transition gear 6 acts as a bridge in the clutch 100 . When the first planetary carrier 52 rotates, the output inner shaft 3 is driven to rotate through the transition gear 6 .

[0052] like Figure 3 As shown, the transition gear 6 is located between the first planetary gear transmission mechanism 5 and the second planetary gear transmission mechanism 7. The setting of the transition gear 6 can also facilitate the assembly of the two planetary gear transmission mechanisms by using the transition gear 6 for transition connection, thereby avoiding excessive interference and assembly difficulty caused by the output inner shaft 3 being too long.

[0053] like Figure 4 As shown, the second planetary gear transmission mechanism 7 includes: a second ring gear 71, a second planet carrier 72 and at least two second planetary gears (not shown).

[0054] The second ring gear 71 and the second planetary carrier 72 are also arranged around the axis L of the clutch 100, providing stable support and rotation space for the second planetary gears. All the second planetary gears are rotatably connected to the second planetary carrier 72, all the second planetary gears are meshed with the transition gear 6, the second planetary carrier 72 is connected to the first ring gear 51, and the second ring gear 71 is connected to the front end of the output shaft sleeve 4. On the one hand, by utilizing the characteristics of the second planetary gear transmission mechanism 7 being in phase power connection with the transition gear 6 and the first ring gear 51, the movement mode of the second planetary gear transmission mechanism 7 is different in the two working states of the flange clutch shaft sleeve 2 being in power connection with the drive device and being out of power connection. On the other hand, the structural characteristics of the planetary gear transmission mechanism itself can be utilized to realize the second deceleration and torque increase of the clutch 100, and the speed decreases when transmitting to the output side.

[0055] Specifically, the first gear ring 51 in the first planetary gear transmission mechanism 5 rotates synchronously with the second planet carrier 72 of the second planetary gear transmission mechanism 7, and the first planet carrier 52 in the first planetary gear transmission mechanism 5 rotates synchronously with the transition gear 6. When the flange clutch sleeve 2 is connected to the driving device by power, the first gear ring 51 and the first planet carrier 52 in the first planetary gear transmission mechanism 5 rotate at the same speed and in the same direction, so that the final output inner shaft 3 and the output sleeve 4 rotate at the same speed and in the same direction. When the flange clutch sleeve 2 is disconnected from the driving device by power, the first gear ring 51 and the first planet carrier 52 in the first planetary gear transmission mechanism 5 rotate at different speeds, so that the final output inner shaft 3 and the output sleeve 4 rotate at different speeds, and the output sleeve 4 rotates at a lower speed than the output inner shaft 3.

[0056] Taking the example shown in the figure as an example, the first ring gear 51 is connected to the flange clutch sleeve 2 and rotates synchronously. Assuming that the direction of the pulley 81 is forward rotation, when the flange clutch sleeve 2 is in the working state of being disconnected from the driving device, the input gear shaft 1 rotates forward. At this time, the first planetary gear transmission mechanism 5 is driven by the meshing transmission of the first planetary gear, driving the first planet carrier 52 to rotate forward and the speed to decrease, and driving the first ring gear 51 to reverse and the speed to decrease. In the second planetary gear transmission mechanism 7, the transition gear 6 and the first planet carrier 52 rotate at the same speed and in the same direction, so the transition gear 6 rotates forward, while the second ring gear 71 reverses. In this way, the output inner shaft 3 finally rotates forward, the output sleeve 4 reverses, and the speed of the output inner shaft 3 is greater than the speed of the output sleeve 4, and the speed of the output inner shaft 3 is less than the speed of the input gear shaft 1. When the flange clutch sleeve 2 is in working state in power connection with the driving device, the first planetary gear transmission mechanism 5 rotates forward at a constant speed, the second planetary gear transmission mechanism 7 rotates forward at a constant speed, and finally the output inner shaft 3 and the output sleeve 4 rotate forward at a constant speed, and the speed is equal to the speed of the input gear shaft 1.

[0057] Therefore, according to the clutch 100 of the new dual-drive washing machine of the embodiment of the utility model, by setting the above-mentioned first planetary gear transmission mechanism 5 and the second planetary gear transmission mechanism 7, when the flange clutch sleeve 2 is switched between the power connection and the power connection of the driving device, two working modes can be obtained. In one working mode, the input gear shaft 1 and the output shaft sleeve 4 output at high speed in the same direction, and in another working mode, the input gear shaft 1 and the output shaft sleeve 4 both output at low speed, and the rotation speeds of the two are not equal. The clutch 100 of the present application has a simple structure, stable and reliable operation, high compactness, and can meet the needs of different working modes of the new dual-drive washing machine. The setting of the two planetary gear transmission mechanisms enables the input gear shaft 1 and the output shaft sleeve 4 to reduce speed and the reduction range is unequal, and it can also achieve two decelerations and torque increases, and the single reduction ratio does not need to be set too high, which is conducive to reducing the impact of operation.

[0058] According to some embodiments of the present invention, the clutch 100 is as follows: Figure 2-Figure 5 As shown, the transition gear 6 is outer-circuited on the front end of the output inner shaft 3 to rotate synchronously, and the first planetary carrier 52 is outer-circuited on the transition gear 6 to rotate synchronously.

[0059] The transition gear 6 can ensure the smooth transmission and conversion of power. Specifically, the transition gear 6 is tightly sleeved on the front end of the output inner shaft 3, and through a tight connection, it realizes synchronous rotation with the output inner shaft 3, thereby effectively transmitting power. At the same time, by setting the transition gear 6, the setting length of the output inner shaft 3 can be shortened, which is convenient for assembly.

[0060] The first planet carrier 52 is covered with the transition gear 6, so that the transition gear 6 and the first planet carrier 52 can also achieve synchronous rotation. This connection method not only ensures the continuous transmission of power, but also enables the first planetary gear transmission mechanism 5 and the second planetary gear transmission mechanism 7 to work together to form an integrated power transmission system. This ensures that the washing machine can operate stably in various working modes and meet the user's laundry needs.

[0061] According to some embodiments of the present application, the clutch 100 is as follows: Figure 2-Figure 5 As shown, the front end of the output inner shaft 3 forms a second gear 31. The output inner shaft 3 not only has the function of power transmission, but also participates in the gear transmission system as a transmission component. The compactness of the clutch 100 is improved, the number of components is reduced, and the cost is reduced and the reliability is improved.

[0062] like Figure 6 As shown, the inner circumference of the transition gear 6 forms transition internal teeth 61, which mesh with the second gear 31 to achieve power transmission between the output inner shaft 3 and the transition gear 6. Since the number of teeth of the transition internal teeth 61 and the second gear 31 is equal, the transmission ratio between the two is one to one, ensuring the smooth transmission of power and the continuity of speed.

[0063] The outer peripheral surface of the transition gear 6 forms a transition outer tooth 62, and the second planetary gear meshes with the transition outer tooth 62 to transmit power to the second planetary gear transmission mechanism 7. The transition gear 6 plays a bridge role in the clutch 100, connecting the two gear transmission mechanisms, and realizing continuous power transmission.

[0064] The inner circumference of the first planet carrier 52 forms the first planet connecting teeth 521, which are sleeved on the transition outer teeth 62 and have the same number of teeth. This allows the first planet carrier 52 and the transition gear 6 to rotate synchronously, ensuring the stable operation of the first planetary gear transmission mechanism 5. At the same time, due to the equal number of teeth, the transmission ratio is maintained at one to one, further ensuring the smooth transmission of power.

[0065] According to some embodiments of the present application, the clutch 100 is as follows: Figure 3-Figure 5 As shown, the first planet carrier 52 includes a first front carrier 522 and a first rear carrier 523 .

[0066] The first front frame 522 and the first tail frame 523 are both distributed along the axial direction. Both parts are annularly arranged around the axis L, which are not only structurally stable, but also capable of supporting and fixing the first planetary gear. The first planetary gear transmission mechanism 5 also includes a first gear shaft 53 through which the first planetary gear is passed, and the two ends of the first gear shaft 53 are respectively connected to the first front frame 522 and the first tail frame 523, thereby ensuring the reliability of the first planetary gear during the rotation process. It is particularly worth mentioning that the first tail frame 523 is directly connected to the transition gear 6, so that the power transmission between the first planetary gear transmission mechanism 5 and the transition gear 6 can be more direct and efficient.

[0067] The structure of the second planetary carrier 72 is similar to that of the first planetary carrier 52, and also includes a second front frame 721 and a second tail frame 723 distributed along the axial direction. These two parts are also annular and arranged around the axis L, providing stable support for the second planetary gear. The second gear shaft 73 in the second planetary gear transmission mechanism 7 passes through the second planetary gear, and its two ends are respectively connected to the second front frame 721 and the second tail frame 723, ensuring the normal operation of the second planetary gear. In addition, the second front frame 721 is connected to the first ring gear 51, so that the first planetary gear transmission mechanism 5 and the second planetary gear transmission mechanism 7 can be closely connected to form an integrated power transmission system.

[0068] In some optional embodiments, such as Figure 2-Figure 5 As shown, a first support column 524 is integrally formed on one of the first front frame 522 and the first tail frame 523. The first support column 524 not only enhances the overall strength of the first planetary frame 52, but also acts as a connecting member.

[0069] The first support column 524 is firmly connected to the other of the first front frame 522 and the first tail frame 523 through a first fastener, such as a bolt or a pin. This connection method is simple and effective, which can not only ensure the structural strength, but also achieve fast assembly and disassembly, thereby improving the maintenance convenience of the clutch 100.

[0070] Likewise, if Figure 5 As shown, in the structure of the second planetary carrier 72, a similar connection method is also adopted. A second support column 7211 is integrally formed on one of the second front frame 721 and the second tail frame 723. This second support column 7211 is similar to the first support column 524 in function and structure, and is used to improve the overall strength and connection stability of the planetary carrier. The second support column 7211 is tightly connected to the other of the second front frame 721 and the second tail frame 723 through a second fastener. This connection method ensures the stability and reliability of the second planetary carrier 72 when rotating at high speed and bearing loads.

[0071] By providing the first support column 524 and the second support column 7211 and connecting with corresponding fasteners, the first planet carrier 52 and the second planet carrier 72 can achieve efficient power transmission while ensuring structural strength. This not only improves the overall performance of the clutch 100, but also extends its service life, providing users with a more reliable and stable laundry experience.

[0072] In some optional embodiments, such as Figure 3-Figure 6 As shown, in the structure of the first planetary carrier 52, in order to ensure the precise fit and stable connection between the first gear shaft 53 and the first front frame 522 and the first tail frame 523, first positioning rings 525 are particularly provided on the surfaces facing each other in a one-to-one correspondence. These first positioning rings 525 not only provide accurate positioning for the first gear shaft 53, but also ensure the stability of the gear shaft when rotating at high speed. By inserting the two ends of the first gear shaft 53 into the two first positioning rings 525, the connection between the first gear shaft 53 and the first planetary carrier 52 is achieved, which not only ensures the smooth power transmission, but also avoids the noise and vibration caused by looseness or misalignment.

[0073] Similarly, a similar positioning method is also adopted in the structure of the second planetary carrier 72. The surfaces of the second front frame 721 and the second tail frame 723 facing each other are provided with second positioning rings 724 in a one-to-one correspondence, and these second positioning rings 724 are similar to the first positioning rings 525 in function and structure. The two ends of the second gear shaft 73 are accurately inserted into the two second positioning rings 724, ensuring the close fit and stable transmission between the second gear shaft 73 and the second planetary carrier 72.

[0074] In some optional embodiments, such as Figure 5-Figure 6 As shown, a clamping groove 7212 is provided on the outer circumferential surface of the second front frame 721. There are a plurality of clamping grooves 7212 which are spaced apart along the circumferential direction to form a uniform annular structure.

[0075] At the same time, Figure 7 As shown, the tail end of the first gear ring 51 is provided with a plurality of latching teeth 514, which are spaced apart along the circumferential direction. The shape and size of the latching teeth 514 match the latching grooves 7212 on the second front frame 721, so that they can be accurately latched into the latching grooves 7212. When the first gear ring 51 and the second front frame 721 are assembled, the plurality of latching teeth 514 will be latched into the plurality of latching grooves 7212 one by one, thereby achieving a tight connection between the two.

[0076] This connection method through the matching of the slot 7212 and the tooth 514 is not only firmly connected, but also relatively convenient to install and remove, thereby improving the assembly efficiency of the clutch 100. At the same time, due to the reasonable connection between the tooth 514 and the slot 7212, they can effectively resist vibration and impact during the power transmission process, thereby ensuring the stable operation of the clutch 100.

[0077] In addition, this connection method can improve assembly efficiency, and the latching teeth 514 can be adaptively inserted into the latching groove 7212, thereby avoiding performance degradation or failure caused by improper assembly.

[0078] According to the clutch 100 of some embodiments, at least one of the first planet carrier 52 and the second planet carrier 72 is provided with a weight-reducing hole.

[0079] By providing the weight-reducing holes, the weight of the first planet carrier 52 and the second planet carrier 72 can be reduced without affecting the structural strength and transmission performance, thereby optimizing the overall performance of the clutch 100 .

[0080] These weight-reducing holes are arranged in non-critical stress-bearing areas of the first planet carrier 52 and the second planet carrier 72, which not only avoids weakening the structural strength of critical parts, but also effectively reduces the overall weight.

[0081] In addition, the weight-reducing holes also help to dissipate heat. When the clutch 100 is running at a high speed, the weight-reducing holes on the planet carrier can provide more heat dissipation channels, help reduce the temperature of the components, and extend the service life of the clutch 100.

[0082] According to some embodiments of the clutch 100, Figure 7 As shown, a matching block 513 is disposed at the front end of the first gear ring 51, and the matching blocks 513 are multiple and arranged at intervals along the circumferential direction, so that the matching of the first gear ring 51 with other components is more convenient.

[0083] A matching opening 5131 is formed on the front side of each matching block 513 , and the shape and size of the matching opening 5131 are matched with those of the corresponding components.

[0084] By setting the matching block 513 and the matching opening 5131, the first gear ring 51 can be quickly and stably positioned when connected with other components, simplifying the assembly process and improving the assembly efficiency. At the same time, this matching method also enhances the firmness of the connection and reduces the risk of loosening or dislocation under high-speed rotation and load.

[0085] According to some embodiments of the present invention, the clutch 100 is as follows: Figure 3-Figure 4 , Figure 8 As shown, the second gear ring 71 includes a large gear ring 711 , a small gear ring 712 and a connecting ring plate 713 .

[0086] The large gear ring 711 surrounds and meshes with the second planetary gear, thereby achieving power transmission.

[0087] The small gear ring 712 surrounds the front end of the output shaft sleeve 4, which forms a tight connection between the small gear ring 712 and the output shaft sleeve 4. The front end of the output shaft sleeve 4 is formed with a third gear 41, and the small gear ring 712 is sleeved on the third gear 41, and the number of teeth of the two is equal. This arrangement ensures that the power transmission between the small gear ring 712 and the output shaft sleeve 4 is efficient and stable, and avoids power loss or vibration caused by mismatching the number of teeth. The connecting ring plate 713 is arranged along the tail end of the large gear ring 711 and connected to the outer periphery of the small gear ring 712.

[0088] A third gear 41 is formed at the front end of the output shaft sleeve 4 , and a small gear ring 712 is sleeved on the third gear 41 and has the same number of teeth.

[0089] Please refer to the attached Figure 1-Figure 5 , describing a clutch 100 according to some embodiments of the present application.

[0090] The clutch 100 includes an input gear shaft 1 , a flange clutch sleeve 2 , an output inner shaft 3 , an output sleeve 4 , a first planetary gear transmission mechanism 5 , a transition gear 6 , a second planetary gear transmission mechanism 7 and a first gear 11 .

[0091] The input gear shaft 1 and the output inner shaft 3 are both arranged along the axis L of the clutch 100 .

[0092] The first gear 11 is arranged at the rear end of the input gear shaft 1. The flange clutch sleeve 2 is sleeved on the input gear shaft 1.

[0093] The front end of the output inner shaft 3 is adjacent to and spaced apart from the first gear 11. The output shaft sleeve 4 is sleeved on the output inner shaft 3.

[0094] The output sleeve 4 includes a third gear 41 formed at a front end of the output sleeve 4 .

[0095] The first planetary gear mechanism 5 includes a first ring gear 51 , a first planet carrier 52 and two first planetary gears.

[0096] The first ring gear 51 and the first planet carrier 52 are arranged around the axis L, all the first planetary gears are rotatably connected to the first planet carrier 52, all the first planetary gears surround and mesh with the first gear 11, all the first planetary gears are meshed with the first ring gear 51, and the first ring gear 51 is connected to the flange clutch sleeve 2.

[0097] The inner circumference of the first planet carrier 52 forms first planet connecting teeth 521 , and the first planet connecting teeth 521 are sleeved on the transition outer teeth 62 and have the same number of teeth.

[0098] The first planetary frame 52 includes a first front frame 522 , a first tail frame 523 , a first positioning ring 525 , and a weight-reducing hole.

[0099] The first front frame 522 and the first tail frame 523 are distributed along the axial direction. The first front frame 522 and the first tail frame 523 are both annularly arranged around the axis L. The first planetary gear transmission mechanism 5 also includes a first gear shaft 53 through which the first planetary gear is passed. The two ends of the first gear shaft 53 are respectively connected to the first front frame 522 and the first tail frame 523, and the first tail frame 523 is connected to the transition gear 6.

[0100] A first support column 524 is integrally formed on the first front frame 522 , and the first support column 524 is connected to the first tail frame 523 via a first fastener.

[0101] First positioning rings 525 are provided one by one on the surfaces of the first front frame 522 and the first tail frame 523 facing each other, and two ends of the first gear shaft 53 are inserted into the two first positioning rings 525 .

[0102] The first gear ring 51 includes latch teeth 514 and a matching block 513 .

[0103] The latching teeth 514 are disposed at the rear end of the first gear ring 51 , and there are a plurality of latching teeth 514 distributed at intervals along the circumferential direction.

[0104] The matching block 513 is disposed at the front end of the first gear ring 51 . There are multiple matching blocks 513 , which are arranged at intervals along the circumferential direction. A matching opening 5131 is formed at the front side of each matching block 513 .

[0105] The second planetary gear mechanism 7 includes a second ring gear 71 , a second planet carrier 72 , at least two second planetary gears and a second gear shaft 73 .

[0106] The second ring gear 71 and the second planet carrier 72 are arranged around the axis L, all the second planetary gears are rotatably connected to the second planet carrier 72, all the second planetary gears surround and mesh with the transition gear 6, all the second planetary gears are meshed with the second ring gear 71, and the second planet carrier 72 is connected to the first ring gear 51.

[0107] The second ring gear 71 includes a large ring gear 711 , a small ring gear 712 and a connecting ring plate 713 .

[0108] The large ring gear 711 surrounds and meshes with the second planetary gears.

[0109] The small gear ring 712 surrounds the front end of the output shaft sleeve 4 , and the small gear ring 712 is sleeved on the third gear 41 and has the same number of teeth.

[0110] The connecting ring plate 713 is disposed along the rear end of the large gear ring 711 and connected to the outer circumference of the small gear ring 712 .

[0111] The second planetary carrier 72 includes a second front carrier 721 , a second tail carrier 723 , a second positioning ring 724 and weight-reducing holes.

[0112] The second front frame 721 and the second tail frame 723 are distributed along the axial direction, and both the second front frame 721 and the second tail frame 723 are in a circular ring shape arranged around the axis L.

[0113] The second gear shaft 73 passes through the second planetary gear, and two ends of the second gear shaft 73 are respectively connected to the second front frame 721 and the second tail frame 723 .

[0114] The second front frame 721 includes a second support column 7211 and a slot 7212 .

[0115] The second support column 7211 is integrally formed on the second front frame 721 , and the second support column 7211 is connected to the second tail frame 723 via a second fastener.

[0116] Second positioning rings 724 are provided one by one on the surfaces of the second front frame 721 and the second tail frame 723 facing each other, and two ends of the second gear shaft 73 are inserted into the two second positioning rings 724 .

[0117] The card slots 7212 are arranged on the outer peripheral surface of the second front frame 721 , and there are a plurality of card slots 7212 which are spaced apart along the circumferential direction.

[0118] The latching teeth 514 of the first gear rings 51 are respectively latched in the latching grooves 7212 , so that the second front frame 721 is connected to the first gear rings 51 .

[0119] The transition gear 6 is outer-circuited on the front end of the output inner shaft 3 to rotate synchronously, and the first planet carrier 52 is outer-circuited on the transition gear 6 to rotate synchronously.

[0120] The front end of the output inner shaft 3 forms a second gear 31 .

[0121] The transition gear 6 includes transition inner teeth 61 and transition outer teeth 62 .

[0122] The transition internal teeth 61 are formed on the inner circumferential surface of the transition gear 6 , and the transition internal teeth 61 are sleeved on the second gear 31 and have the same number of teeth.

[0123] The transition external teeth 62 are formed on the outer peripheral surface of the transition gear 6 , and the second planetary gears mesh with the transition external teeth 62 .

[0124] Other components of the clutch 100 according to the embodiment of the present invention, such as a washing machine, are known to those skilled in the art and will not be described in detail here.

[0125] In the description of this specification, the description with reference to the terms "embodiment", "example", etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the utility model. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0126] Although the embodiments of the present invention have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A new dual-drive washing machine clutch, characterized in that: The clutch (100) comprises: An input gear shaft (1), the input gear shaft (1) being arranged along an axis (L) of the clutch (100), and a first gear (11) being arranged at a rear end of the input gear shaft (1); A flange clutch sleeve (2), wherein the flange clutch sleeve (2) is sleeved on the input gear shaft (1); an output inner shaft (3), the output inner shaft (3) being arranged along the axis (L), the front end of the output inner shaft (3) being adjacent to and spaced apart from the first gear (11); An output shaft sleeve (4), wherein the output shaft sleeve (4) is sleeved on the output inner shaft (3); A first planetary gear transmission mechanism (5), the first planetary gear transmission mechanism (5) comprising: a first ring gear (51), a first planet carrier (52) and at least two first planetary wheels, the first ring gear (51) and the first planet carrier (52) being arranged around the axis (L), all the first planetary wheels being rotatably connected to the first planet carrier (52), all the first planetary wheels being around and meshing with the first gear (11), all the first planetary wheels being meshing with the first ring gear (51), and the first ring gear (51) or the first planet carrier (52) being connected to the flange clutch sleeve (2); A transition gear (6), the transition gear (6) being connected to the front end of the output inner shaft (3) and the first planet carrier (52); A second planetary gear transmission mechanism (7), the second planetary gear transmission mechanism (7) comprising: a second ring gear (71), a second planet carrier (72) and at least two second planetary wheels, the second ring gear (71) and the second planet carrier (72) are arranged around the axis (L), all the second planetary wheels are rotatably connected to the second planet carrier (72), all the second planetary wheels surround and mesh with the transition gear (6), all the second planetary wheels are meshed with the second ring gear (71), the second planet carrier (72) is connected to the first ring gear (51), and the second ring gear (71) is connected to the front end of the output shaft sleeve (4).

2. The new dual-drive washing machine clutch according to claim 1 is characterized in that: The transition gear (6) is externally mounted on the front end of the output inner shaft (3) to rotate synchronously, and the first planet carrier (52) is externally mounted on the transition gear (6) to rotate synchronously.

3. The new dual-drive washing machine clutch according to claim 2 is characterized in that: The front end of the output inner shaft (3) forms a second gear (31), the inner circumferential surface of the transition gear (6) forms transition internal teeth (61), and the transition internal teeth (61) are sleeved on the second gear (31) and have the same number of teeth; The outer peripheral surface of the transition gear (6) forms transition external teeth (62), and the second planetary gear is meshed with the transition external teeth (62); The inner circumferential surface of the first planet carrier (52) forms first planet connecting teeth (521), and the first planet connecting teeth (521) are sleeved on the transition external teeth (62) and have the same number of teeth.

4. The novel dual-drive washing machine clutch according to claim 1 is characterized in that: The first planetary frame (52) comprises: a first front frame (522) and a first tail frame (523) distributed along the axial direction, the first front frame (522) and the first tail frame (523) are both in the shape of an annular ring arranged around the axis (L), the first planetary gear transmission mechanism (5) also comprises a first gear shaft (53) passing through the first planetary gear, the two ends of the first gear shaft (53) are respectively connected to the first front frame (522) and the first tail frame (523), and the first tail frame (523) is connected to the transition gear (6); The second planetary frame (72) comprises: a second front frame (721) and a second tail frame (723) distributed along the axial direction, the second front frame (721) and the second tail frame (723) are both in the shape of an annular ring arranged around the axis (L), the second planetary gear transmission mechanism (7) also comprises a second gear shaft (73) passing through the second planetary gear, the two ends of the second gear shaft (73) are respectively connected to the second front frame (721) and the second tail frame (723), and the second front frame (721) is connected to the first ring gear (51).

5. The novel dual-drive washing machine clutch according to claim 4 is characterized in that: A first support column (524) is integrally formed on one of the first front frame (522) and the first tail frame (523), and the first support column (524) is connected to the other of the first front frame (522) and the first tail frame (523) through a first fastener; A second support column (7211) is integrally formed on one of the second front frame (721) and the second tail frame (723), and the second support column (7211) is connected to the other of the second front frame (721) and the second tail frame (723) via a second fastener.

6. The novel dual-drive washing machine clutch according to claim 4 is characterized in that: The surfaces of the first front frame (522) and the first tail frame (523) facing each other are provided with first positioning rings (525) in a one-to-one correspondence, and the two ends of the first gear shaft (53) are inserted into the two first positioning rings (525); Second positioning rings (724) are provided one-to-one on surfaces of the second front frame (721) and the second tail frame (723) facing each other, and two ends of the second gear shaft (73) are inserted into the two second positioning rings (724).

7. The novel dual-drive washing machine clutch according to claim 4 is characterized in that: The outer circumferential surface of the second front frame (721) is provided with a card slot (7212), and the card slots (7212) are multiple and distributed at intervals along the circumferential direction; The tail end of the first gear ring (51) is provided with a latching tooth (514), the latching teeth (514) being multiple and distributed at intervals along the circumferential direction, and the multiple latching teeth (514) are respectively latched in the multiple latching grooves (7212).

8. The novel dual-drive washing machine clutch according to claim 1 is characterized in that: At least one of the first planet carrier (52) and the second planet carrier (72) is provided with a weight-reducing hole.

9. The novel dual-drive washing machine clutch according to claim 1 is characterized in that: A matching block (513) is provided at the front end of the first gear ring (51). The matching blocks (513) are multiple and arranged at intervals along the circumferential direction. A matching opening (5131) is formed on the front side of each matching block (513).

10. The novel dual-drive washing machine clutch according to any one of claims 1 to 9, characterized in that: The second gear ring (71) comprises: A large gear ring (711), the large gear ring (711) surrounds and meshes with the second planetary gear; A small gear ring (712), the small gear ring (712) surrounds the front end of the output shaft sleeve (4); A connecting ring plate (713), wherein the connecting ring plate (713) is arranged along the rear end of the large gear ring (711) and connected to the outer periphery of the small gear ring (712); Wherein, a third gear (41) is formed at the front end of the output shaft sleeve (4), and the small gear ring (712) is sleeved on the third gear (41) and has the same number of teeth.

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