Unidirectional transmission planet carrier for hub motor

Abstract

The utility model belongs to the technical field of hub motors, and discloses a one-way transmission planet carrier for a hub motor, which comprises a fixedly arranged planet carrier inner ring. A planet carrier outer ring which is coaxially arranged is arranged on the outer side of the planet carrier inner ring, a plurality of shaft columns are connected to the upper end of the planet carrier outer ring, the shaft columns and the planet carrier outer ring are coaxially arranged, the shaft columns are annularly and uniformly distributed around the central axis of the planet carrier outer ring, and the shaft columns are used for mounting planet wheels; an annular raceway is formed between the outer side wall of the planet carrier inner ring and the inner side wall of the planet carrier outer ring; a plurality of cylindrical rollers are arranged in the roller path, the cylindrical rollers and the planet carrier inner ring are coaxially arranged, and the width of the roller path in the radial direction of the planet carrier inner ring is equal to the diameter of the cylindrical rollers; a plurality of special-shaped rollers are arranged in the roller path, and the special-shaped rollers and the cylindrical rollers are coaxially arranged; the problems that in the prior art, a one-way transmission planet carrier is unstable in rotation and large in vibration noise due to separation of an inner ring and an outer ring are solved.

Description

Technical Field

[0001] This utility model belongs to the field of hub motor technology, specifically relating to a unidirectional transmission planetary carrier for hub motors. Background Technology

[0002] In the design of unidirectional planetary carriers for hub motors, the traditional cylindrical roller structure has significant technical limitations. This type of unidirectional clutch achieves its locking function based on the wedge-tight fit between the rollers and the inclined raceway. Its inherent structure inevitably leads to operating clearance during free rotation. Specifically, to achieve unidirectional locking, the rollers must be tightly fitted with the inner and outer rings in the locked state, and completely release the contact pressure in the disengaged state. This working principle causes the inner and outer rings of the planetary carrier to lose mechanical connection during free rotation. Furthermore, considering manufacturing tolerances and assembly requirements, a 0.1-0.3mm clearance must be maintained between the rollers and the raceway, further exacerbating the radial clearance problem. When the hub motor operates at high speed, this structural defect causes relative runout between the inner and outer rings of the planetary carrier, resulting not only in significant vibration and noise but also rapid wear of the contact surfaces due to impact loads. More seriously, the separation of the inner and outer rings of the planetary carrier in traditional designs directly affects the smoothness of power transmission, severely restricting the overall performance of the hub motor. Therefore, existing technologies suffer from unstable rotation and high vibration and noise caused by the separation of the inner and outer rings in unidirectional planetary carriers. Utility Model Content

[0003] In view of the shortcomings of the prior art, the purpose of this utility model is to provide a one-way transmission planetary carrier for hub motors, which solves the problems of unstable rotation and high vibration and noise caused by the separation of inner and outer rings in the existing one-way transmission planetary carrier.

[0004] The objective of this utility model can be achieved through the following technical solutions:

[0005] A unidirectional transmission planetary carrier for a hub motor includes a fixedly disposed inner ring of the planetary carrier.

[0006] The planetary carrier inner ring is provided with a planetary carrier outer ring placed on the same axis. Multiple shafts are connected to the upper end of the planetary carrier outer ring. The shafts are all placed on the same axis as the planetary carrier outer ring. The multiple shafts are evenly distributed in a ring around the central axis of the planetary carrier outer ring. The shafts are all used to install planetary gears.

[0007] An annular raceway is formed between the outer wall of the inner ring of the planet carrier and the inner wall of the outer ring of the planet carrier;

[0008] The raceway contains multiple cylindrical rollers, all of which are placed coaxially with the inner ring of the planetary carrier. The width of the raceway along the radial direction of the inner ring of the planetary carrier is equal to the diameter of the cylindrical rollers.

[0009] The raceway is equipped with multiple irregular rollers, which are placed coaxially with the cylindrical rollers. The outer side wall of the inner ring of the planetary carrier and the inner side wall of the outer ring of the planetary carrier are always in contact with the irregular rollers, and each irregular roller has the same contact posture with respect to the inner ring and outer ring of the planetary carrier.

[0010] The irregular roller is a cylindrical body with a uniform cross-section along the axial direction, and the maximum cross-sectional width along the axial direction is greater than the diameter of the cylindrical roller;

[0011] As the shaped rollers deflect, the width of the shaped rollers along the radial direction of the outer ring of the planetary carrier gradually increases or decreases.

[0012] The outer ring of the planetary carrier has end plates at both ends along its own axis. The end plates are used to cover the raceway. The two end plates and the outer ring of the planetary carrier are fixedly connected as one unit by multiple connectors.

[0013] There are multiple cylindrical rollers, and these multiple cylindrical rollers are evenly distributed in a ring around the central axis of the inner ring of the planetary carrier.

[0014] The number of irregular rollers between any two adjacent cylindrical rollers is equal, and the irregular rollers between any two adjacent cylindrical rollers are distributed at equal intervals.

[0015] The cross-section of the irregular roller along the axial direction is a parallelogram shape.

[0016] The four corners of the parallelogram cross-section of the irregular roller are all rounded and chamfered.

[0017] The cross-section of the irregular roller along the axial direction is cam end face.

[0018] Each end plate is provided with a through hole that is placed coaxially with the inner ring of the planet carrier. The diameter of the through hole is smaller than the diameter of the outer peripheral wall of the inner ring of the planet carrier, and the diameter of the through hole is greater than or equal to the diameter of the inner peripheral wall of the inner ring of the planet carrier.

[0019] The beneficial effects of this utility model are:

[0020] This invention integrates the dual functions of a one-way bearing and a planetary gear carrier. It also features an innovative design where the inner and outer rings of the planetary carrier are coaxially arranged to form an annular raceway. Cylindrical rollers and shaped rollers are simultaneously arranged within this raceway. The shaped rollers' uniform cross-section and greater width than cylindrical rollers ensure continuous contact between the inner and outer rings of the planetary carrier. This optimizes contact stress distribution, significantly improves load-bearing capacity and wear resistance, and creates a stable support structure. This effectively solves the problem of unstable rotation caused by the separation of the inner and outer rings in traditional one-way clutches, greatly reducing operating vibration and noise. When the outer ring of the planetary carrier rotates, the shaped rollers, through their unique radial width adjustable mechanism, ensure reliable locking performance under high-speed operation and variable load conditions, fundamentally overcoming the failure risk of traditional clutches under complex operating conditions. This integrated design comprehensively improves the overall performance of the one-way clutch while maintaining its original deceleration function. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, for those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0022] Figure 1 This is a schematic diagram of the overall structure of this utility model;

[0023] Figure 2 These are schematic diagrams of the overall structure of this utility model from different perspectives;

[0024] Figure 3 This is a partial structural diagram of the irregular roller part of this utility model;

[0025] Figure 4 This is a schematic diagram of a portion of the raceway structure of this utility model. Detailed Implementation

[0026] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of the present utility model.

[0027] This combination Figures 1 to 4This invention describes an embodiment of a one-way drive planetary carrier for a hub motor. Specifically, the one-way drive planetary carrier for a hub motor is constructed as a split structure, comprising components such as an inner ring 100, an outer ring 200, a raceway 300, cylindrical rollers 400, a shaft post 800, and shaped rollers 500. In this application, the inner ring 100 and the outer ring are coaxially arranged to form an annular raceway 300. Cylindrical rollers 400 and shaped rollers 500 are simultaneously arranged within the raceway 300. The uniform cross-section design of the shaped rollers 500, combined with their maximum width being greater than the diameter of the cylindrical rollers 400, ensures a more uniform distribution of contact stress through continuous contact between the inner and outer rings of the planetary carrier, directly improving the performance of traditional one-way clutches. The insufficient number of rollers leads to low load-bearing capacity and easy wear. The stable support structure formed by the special-shaped roller 500 and the inner and outer rings of the planetary carrier effectively reduces the rotational instability caused by the separation of the inner and outer rings in the traditional design, and significantly reduces the vibration and noise levels during operation. When the outer ring 200 of the planetary carrier rotates, the reliable deflection mechanism of the special-shaped roller 500 makes its radial width adjustable. This feature ensures stable locking performance under high-speed operation and load changes, effectively solving the failure risk of traditional clutches under complex working conditions. This integrated design systematically improves the overall performance of the one-way clutch while maintaining the deceleration function.

[0028] Please refer to Figures 1 to 4 A unidirectional transmission planetary carrier for a hub motor includes a fixedly disposed inner ring 100 of the planetary carrier;

[0029] The outer ring 200 of the planetary carrier is coaxially placed on the outer side of the inner ring 100 of the planetary carrier. Multiple shafts 800 are connected to the upper end of the outer ring 200 of the planetary carrier. The shafts 800 are all coaxially placed with the outer ring 200 of the planetary carrier. The multiple shafts 800 are evenly distributed in a ring around the central axis of the outer ring 200 of the planetary carrier. The shafts 800 are all used to install planetary gears.

[0030] An annular raceway 300 is formed between the outer sidewall of the inner ring 100 of the planet carrier and the inner sidewall of the outer ring 200 of the planet carrier.

[0031] The raceway 300 is provided with multiple cylindrical rollers 400, all of which are placed coaxially with the inner ring 100 of the planetary carrier. The width of the raceway 300 along the radial direction of the inner ring 100 of the planetary carrier is equal to the diameter of the cylindrical rollers 400.

[0032] Multiple irregular rollers 500 are provided in the raceway 300. The irregular rollers 500 and the cylindrical rollers 400 are placed coaxially. The outer side wall of the inner ring 100 of the planetary carrier and the inner side wall of the outer ring 200 of the planetary carrier are always in contact with the irregular rollers 500, and each irregular roller 500 has the same contact posture with respect to the inner ring 100 and the outer ring 200 of the planetary carrier.

[0033] The shaped roller 500 is a cylindrical body with a uniform cross-section along the axial direction, and the maximum cross-sectional width along the axial direction is greater than the diameter of the cylindrical roller 400.

[0034] When the shaped roller 500 deflects, the width of the shaped roller 500 in the radial direction along the outer ring 200 of the planetary carrier gradually increases or decreases.

[0035] In use, the inner ring 100 of the planetary carrier is fixedly connected to the outside; the outer ring 200 of the planetary carrier is used to connect the sun gear and other components for rotation.

[0036] When the outer ring 200 of the planetary carrier rotates, the change in the width of the shaped roller 500 along the radial direction of the outer ring 200 of the planetary carrier can be set according to actual needs. By adjusting the contact posture of each shaped roller 500 relative to the inner ring 100 and the outer ring 200 of the planetary carrier during production, the relationship between the change in the width of the shaped roller 500 along the radial direction of the outer ring 200 of the planetary carrier and the rotation direction of the outer ring of the planetary carrier can be controlled.

[0037] When the outer ring 200 of the planetary carrier rotates in a certain direction, the shaped roller 500 deflects and its width gradually decreases along the radial direction of the outer ring 200 of the planetary carrier.

[0038] For ease of description, in this embodiment, when the outer ring 200 of the planetary carrier rotates counterclockwise and drives the shaped roller 500 to deflect, the width of the shaped roller 500 along the radial direction of the outer ring 200 gradually decreases; when the outer ring 200 of the planetary carrier rotates clockwise, the shaped roller 500 deflects and its width along the radial direction of the outer ring 200 gradually increases; thus, in this embodiment, the outer ring 200 of the planetary carrier can rotate freely when it rotates counterclockwise; when the outer ring 200 of the planetary carrier rotates clockwise, under the action of friction, the outer ring 200 of the planetary carrier drives the shaped roller 500 to deflect, the width of the shaped roller 500 along the radial direction of the outer ring 200 gradually increases, and the shaped roller 500 abuts against and locks the inner and outer rings, thereby locking the rotation of the outer ring 200 of the planetary carrier.

[0039] This application employs a planetary carrier inner ring 100 and outer ring coaxially arranged to form an annular raceway 300. Cylindrical rollers 400 and shaped rollers 500 are simultaneously arranged within the raceway 300. The uniform cross-section design of the shaped rollers 500, combined with their maximum width exceeding the diameter of the cylindrical rollers 400, ensures a more uniform distribution of contact stress through continuous contact between the inner and outer rings of the planetary carrier. This directly improves the low load-bearing capacity and easy wear problems caused by insufficient roller count in traditional one-way clutches. The stable support structure formed by the shaped rollers 500 and the inner and outer rings of the planetary carrier effectively reduces the rotational instability caused by the separation of the inner and outer rings in traditional designs, significantly reducing vibration and noise levels during operation. When the outer ring 200 of the planetary carrier rotates, the reliable deflection mechanism of the shaped rollers 500 allows for adjustable radial width. This feature ensures stable locking performance under high-speed operation and load changes, effectively solving the failure risk of traditional clutches under complex working conditions. This integrated design systematically improves the overall performance of the one-way clutch while maintaining its deceleration function.

[0040] The planetary carrier outer ring 200 has end plates 600 at both ends along its own axis. The end plates are used to cover the raceway 300. The two end plates 600 and the planetary carrier outer ring 200 are fixedly connected as one unit by multiple connectors 700. The end plates 600 are used to prevent the cylindrical rollers 400 and the irregular rollers 500 from falling off and separating from the raceway 300.

[0041] Preferably, the connector 700 can be made of rivets, bolts, etc.

[0042] There are multiple cylindrical rollers 400, and the multiple cylindrical rollers 400 are evenly distributed in a ring around the central axis of the inner ring 100 of the planetary carrier. By setting multiple cylindrical rollers 400, not only is the frictional force between the inner ring 100 and the outer ring 200 of the planetary carrier effectively reduced, but the concentricity of the inner ring 100 and the outer ring 200 of the planetary carrier is also effectively guaranteed.

[0043] The number of irregular rollers 500 between any two adjacent cylindrical rollers 400 is equal, and the irregular rollers 500 between any two adjacent cylindrical rollers 400 are distributed at equal intervals; the densely distributed irregular rollers 500 can effectively improve the load-bearing capacity of the hub motor, and the equal number and equal spacing of the arrangement can effectively improve the balance of the working state.

[0044] The profiled roller 500 has a parallelogram-shaped cross section along the axial direction. This parallelogram-shaped cross section, combined with the rounded chamfered profiled roller 500 design, significantly improves the dynamic performance of the transmission system through its unique geometric features: the inclined side structure of the parallelogram generates a progressive contact force when the roller deflects, making the locking process smoother and avoiding the impact vibration of traditional designs.

[0045] The 500 parallelogram cross-section of the irregular roller has rounded chamfers at all four corners. These rounded chamfers not only eliminate stress concentration points and extend the service life of the roller, but also form an effective lubricating oil film retention area, reducing operating noise. At the same time, the axial component force generated by this cross-sectional shape during deflection promotes the circulation and distribution of lubricating oil, enabling the system to maintain stable locking performance even at high speeds. This makes it particularly suitable for hub motor applications that require frequent starts and stops and high speed ratios.

[0046] Preferably, the cross-section of the irregular roller 500 along the axial direction can also be set as a cam end face or an ellipse.

[0047] Each end plate 600 is provided with a through hole 601 placed coaxially with the inner ring 100 of the planetary carrier. The diameter of the through hole 601 is smaller than the diameter of the outer peripheral wall of the inner ring 100 of the planetary carrier, and the diameter of the through hole 601 is greater than or equal to the diameter of the inner peripheral wall of the inner ring 100 of the planetary carrier. The through hole 601 provides space for fixing the inner ring 100 of the planetary carrier to external components.

[0048] In the description of this specification, references to terms such as "an embodiment," "example," "specific example," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0049] The foregoing has shown and described the basic principles, main features, and advantages of this utility model. Those skilled in the art should understand that this utility model is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of this utility model. Various changes and modifications can be made to this utility model without departing from its spirit and scope, and all such changes and modifications fall within the scope of the claims of this utility model.

Claims

1. A unidirectional transmission planetary carrier for a hub motor, comprising a fixedly disposed inner ring (100) of the planetary carrier, characterized in that: The outer ring of the planetary carrier (200) is coaxially placed on the outside of the inner ring (100). Multiple shafts (800) are connected to the upper end of the outer ring (200). The shafts (800) are all coaxially placed with the outer ring (200). The multiple shafts (800) are evenly distributed in a ring around the central axis of the outer ring (200). The shafts (800) are all used to install planetary gears. An annular raceway (300) is formed between the outer wall of the inner ring (100) of the planet carrier and the inner wall of the outer ring (200) of the planet carrier; Multiple cylindrical rollers (400) are provided in the raceway (300). The cylindrical rollers (400) are all placed coaxially with the inner ring (100) of the planetary carrier. The width of the raceway (300) along the radial direction of the inner ring (100) of the planetary carrier is equal to the diameter of the cylindrical rollers (400). Multiple shaped rollers (500) are provided in the raceway (300). The shaped rollers (500) and the cylindrical rollers (400) are placed coaxially. The outer side wall of the inner ring (100) of the planetary carrier and the inner side wall of the outer ring (200) of the planetary carrier are always in contact with the shaped rollers (500), and each shaped roller (500) has the same contact posture with respect to the inner ring (100) and the outer ring (200) of the planetary carrier. The shaped roller (500) is a cylindrical body with a uniform cross-section along the axial direction, and the maximum cross-sectional width along the axial direction is greater than the diameter of the cylindrical roller (400). As the shaped roller (500) deflects, the width of the shaped roller (500) in the radial direction of the outer ring (200) of the planetary carrier gradually increases or decreases.

2. The unidirectional transmission planetary carrier for a hub motor according to claim 1, characterized in that, The planetary carrier outer ring (200) has end plates (600) at both ends along its own axis. The end plates are used to cover the raceway (300). The two end plates (600) and the planetary carrier outer ring (200) are fixedly connected as a whole by multiple connectors (700).

3. The unidirectional transmission planetary carrier for a hub motor according to claim 2, characterized in that, There are multiple cylindrical rollers (400), and the multiple cylindrical rollers (400) are evenly distributed in a ring around the central axis of the inner ring (100) of the planetary carrier.

4. The unidirectional transmission planetary carrier for a hub motor according to claim 3, characterized in that, The number of irregular rollers (500) between any two adjacent cylindrical rollers (400) is equal, and the irregular rollers (500) between any two adjacent cylindrical rollers (400) are distributed at equal intervals.

5. The unidirectional transmission planetary carrier for a hub motor according to claim 1, characterized in that, The cross-section of the irregular roller (500) along the axial direction is a parallelogram shape.

6. The unidirectional transmission planetary carrier for a hub motor according to claim 5, characterized in that, The four corners of the parallelogram cross-section of the irregular roller (500) are all rounded and chamfered.

7. The unidirectional transmission planetary carrier for a hub motor according to claim 1, characterized in that, The cross-section of the irregular roller (500) along the axial direction is cam end face.

8. The unidirectional transmission planetary carrier for a hub motor according to claim 1, characterized in that, Each end plate (600) is provided with a through hole (601) placed coaxially with the inner ring (100) of the planetary carrier. The diameter of the through hole (601) is smaller than the diameter of the outer peripheral wall of the inner ring (100) of the planetary carrier, and the diameter of the through hole (601) is greater than or equal to the diameter of the inner peripheral wall of the inner ring (100) of the planetary carrier.

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