CN214647324U

CN214647324U - Internal speed-changing hub

Info

Publication number: CN214647324U
Application number: CN202120060227.0U
Authority: CN
Inventors: 王晓鸿; 武志国; 胡京城
Original assignee: Kunshan Karasawa Clean Energy Technology Co ltd
Current assignee: Kunshan Karasawa Clean Energy Technology Co ltd
Priority date: 2021-01-11
Filing date: 2021-01-11
Publication date: 2021-11-09
Anticipated expiration: 2031-01-11

Abstract

The utility model belongs to the vehicle field discloses an interior variable speed flower-drum, include: a shaft; the hub shell is rotatably arranged on the shaft and is used for driving the wheel to rotate; a primary driving body rotatably mounted on the shaft and partially received in the hub housing for driving the hub housing; the primary pawl is arranged on the primary driving body and meshed with a primary toothed ring on the inner wall of the hub shell to drive the hub shell. Compared with the prior art, the axial space of the technical scheme is smaller, so that the hub is suitable for a vehicle with a middle-arranged motor and has better sealing performance.

Description

Internal speed-changing hub

Technical Field

The utility model belongs to the vehicle field, in particular to improvement to having interior variable speed function vehicle flower-drum.

Background

The existing automatic internal speed change has large axial size and cannot be directly applied to single-armed vehicles and central motors. And because the axial size is larger, the automatic internal speed change adopts a bead gear structure, so that the ampere and the maintenance are inconvenient.

Referring to the inner speed change hub shown in fig. 1, when the speed is lowest in one stage of driving, the power of the driving body 102 is transmitted to the other end in the axial direction through the axial transmission assembly 106, and the hub shell is driven through the claw seat body 104 at the other end in the axial direction and the pawls 108 on the claw seat body 104.

Because the axial rotation structure is large, the drum shaft is subjected to large shearing force, in order to avoid the influence of the shearing force on the drum shaft, a ball stop structure must be used between the driving body 102 and the claw seat body 106 and the drum shaft, and the structure is not easy to prevent water. And the lengthy axial structure cannot be combined with the mid-motor structure.

SUMMERY OF THE UTILITY MODEL

The utility model aims at: the axial size is reduced, and the contact ball baffle is converted into a bearing scheme, so that automatic inner two-speed mounting into a single arm or a built-in motor is realized, and meanwhile, the sealing performance is improved, and the invasion of rainwater, dust, oil dirt and the like is also avoided.

For solving the problem the utility model provides an interior variable speed flower-drum includes:

a shaft;

the hub shell is rotatably arranged on the shaft and is used for driving the wheel to rotate;

a primary driving body rotatably mounted on the shaft and partially received in the hub housing for driving the hub housing;

the primary pawl is arranged on the primary driving body and meshed with a primary toothed ring on the inner wall of the hub shell to drive the hub shell.

As a further improvement of an embodiment of the present application, the primary pawl is elastically resettably fixed to the primary drive body.

As a further improvement of an embodiment of the present application, the primary pawl is fixed to the primary driving body by an elastic snap ring; the surface of the primary driver is provided with a concave part for accommodating the primary pawl, and the surface of the primary pawl is provided with a groove for fixing the elastic snap ring; the primary driving surface is provided with a groove which can be fixed through the elastic clamping ring.

As a further improvement of an embodiment of the present application, the primary pawl includes an engaging portion that engages with the primary toothed ring, and a rotating portion for providing a rotational fulcrum of the primary pawl, the rotating portion having an arc-shaped surface; a cavity for accommodating and allowing the rotating part to rotate therein is arranged in the concave part of the surface of the driving body.

As a further improvement of an embodiment of the present application, the planetary gear set further includes a secondary driving body, and the primary driving body and the secondary driving body are connected through a planetary gear set; the primary driving body drives the secondary driving body to rotate at an increased speed through the planetary gear set.

As a further improvement of an embodiment of the present application, the shaft is provided with a sun gear of the planetary gear set; the primary driving body is provided with a star wheel meshed with the sun wheel; the secondary driving body is provided with a gear ring meshed with the star wheel; when the star wheel rotates, the first-stage driving body drives the star wheel to rotate, and the star wheel drives the gear ring to rotate at an increased speed; and the gear ring drives the secondary driving body to integrally rotate.

As a further improvement of an embodiment of the present application, the secondary driving body includes a centrifugal block rotating with the ring gear, a clutch plate driven by the centrifugal block, and a secondary pawl; when the rotating speed is increased, the centrifugal block rotates along the fixed shaft of the centrifugal block and drives the clutch plate; the clutch plate rotates along with the centrifugal block and drives the secondary pawl to be meshed with a secondary toothed ring on the inner wall of the shell; when the rotating speed is reduced, the centrifugal block drive, the clutch plate and the secondary pawl reset respectively.

As a further improvement of an embodiment of the present application, the clutch plate includes a pawl slot for accommodating the secondary pawl, the pawl slot includes a first accommodating portion and a second accommodating portion that are communicated with each other, and the second accommodating portion is located at a radial outer side of the first accommodating portion; the clutch plate is driven by the centrifugal block, and the secondary pawl enters the second accommodating part from the first accommodating part; when the clutch plate is reset, the pawl enters the first accommodating part from the second accommodating part.

As a further improvement of an embodiment of the present application, the centrifugal block is fixed on the secondary driving body by a fixed shaft; the fixed shaft is provided with a torsion spring for providing a reset force for resetting the centrifugal block; the centrifugal block is provided with a driving shaft connected with the clutch plate, and the driving shaft drives the clutch plate to rotate when the centrifugal block rotates around the fixed shaft.

As a further improvement of an embodiment of the present application, a transmission gear ring engaged with the secondary pawl is provided in the hub housing, and the transmission gear ring is engaged with the secondary gear ring.

According to the technical scheme, the integral-level driving body is integrated with the pawl, so that a pawl seat body at the other axial end and structures such as an anti-rotation gasket, a wave spring and a clamp spring which are matched with each other are omitted. The axial space is greatly saved.

The existing driving body needs to be firstly meshed with the claw seat body through the spline and then the claw seat body drives the pawl, and the pawl drives the toothed ring on the hub shell to drive the hub to rotate, so that the power multistage transmission loss is high. And the utility model discloses a one-level transmission is direct to be conducted to the one-level pawl through the driving body, thereby the pawl drives the one-level ring gear on the flower-drum shell and drives the flower-drum rotation, and the direct transmission efficiency of power is high.

And the rotation risk caused by the possible connection problem of the driving body and the claw seat body connecting spline is also avoided. And the shearing force applied to the hub shaft caused by the claw seat body after the claw seat body is removed is also eliminated directly, the abrasion to the bearing is smaller, and a ball bearing can be used, so that better sealing performance is provided.

In the aspect of application: the structure cancels the original inner two-speed independent claw seat body structure, and solves the problem of larger axial length of automatic speed change by a unique pawl structure and driving body integration mode. The structure also meets the requirement of the middle-mounted motor on the axial space, thereby providing a brand-new solution for the physical speed change of the middle-mounted motor. The bicycle is used for a single-arm bicycle, and has the characteristics of attractive appearance, simplicity, convenience, easy maintenance, comfortable riding and good water resistance.

Drawings

Fig. 1 is a schematic view of a prior art internal shift hub.

Fig. 2 is a schematic perspective view of an internal shift hub.

FIG. 3 is a schematic cross-sectional view of the inner hub taken along the line A-A shown in FIG. 2.

Fig. 4 is an axial exploded view and a partial enlarged view of the inner hub.

Fig. 5 is a schematic perspective view of a primary driver.

Fig. 6 is a side view schematically illustrating a secondary driving body.

Fig. 7 is a side view of a secondary driving body, wherein a centrifugal mass shown in fig. 6 is omitted.

Fig. 8 is a side view of the secondary driving body, wherein two centrifugal weights and clutch plates shown in fig. 6 are omitted.

Detailed Description

The technical solution of the present invention will be further elaborated with reference to the drawings.

Referring to fig. 2, a perspective view of a hub 200 is shown, wherein a motor or a bicycle freewheel structure coupled to a primary drive body 202 is omitted.

The hub 200 is used to drive the wheels of a bicycle, an electric vehicle, or the like. The inner hub 200 is shown as supporting a shaft 204. The end of the shaft 204 is fixed to a fork of a bicycle, an electric vehicle, or the like. An internal thread structure 206 for fixing is arranged in the shaft 204, and a fixing screw rod meshed with the internal thread structure 206 can be arranged on the fork arm of the vehicle. The primary driving body 202 on the hub 200 is driven by a power source such as a flywheel or a motor of the vehicle to drive the primary driving body 202 to drive the hub shell 208, and the hub shell 208 further drives the wheels to enable the vehicle to run.

The planetary drive arrangement and the centrifugal mass arrangement in fig. 3 are not axially symmetrical in cross-section.

The hub housing 208 and the primary drive body 202 are rotatably mounted on the shaft 204. The end of the hub shell 208 distal from the primary drive body 202 as shown in FIG. 3 is mounted on the shaft 204 via a bearing 302; the shaft 204 is provided with an axial step 304 that prevents the bearing from moving, and the bearing 302 is axially fixed by an external nut 306 and the axial step. The other end of the hub shell 208 is connected to the primary drive body 202 via a bearing 308, and the interior of the primary drive body 202 is connected to the shaft 204 via a bearing 310. It can be seen that the hub housing 208 and the portion of the primary drive body 202 coupled to the bearing 308 are provided with bearing receiving steps or recesses that cooperate to prevent axial movement of the bearing (302, 308, 310), the hub housing 208, and the primary drive body 202. A part of the primary drive body 202 is accommodated in the hub housing 208, and a fixing screw 312 is provided on an end of the primary drive body 20 away from the hub housing 20, and the fixing screw 312 can be used to fix a flywheel for driving the primary drive body 202 to rotate.

Fig. 4 is an exploded view of the variable speed hub 200, wherein the hub shell 208 and the primary drive body 202 are exploded, and the primary drive body 202 and the secondary drive body 320 are not exploded.

Referring to fig. 3 and 4, the primary driving body 202 is provided with a primary pawl 402 for driving the hub shell 208 to rotate. The surface of the primary driving body 202 is provided with a pawl seat 410, the pawl seat 410 is a step structure with a slightly smaller diameter on the surface of the primary driving body 202, and a concave part 404 is arranged on the pawl seat 410, and the concave part 404 is used for accommodating the primary pawl 402. The primary pawl 402 includes a rotary portion 408 and an engagement portion 406, and a cavity is provided in the recess 404 that receives and allows the rotary portion 408 to rotate therein. The pawls are fixed on the pawl seat 410 by an elastic clip 502 (refer to fig. 5), in a natural state, the front end engagement portion 406 of the primary pawl 402 is tilted upward under the pressure of the elastic clip ring 502, the tilted front end is engaged with the primary toothed ring 412 on the inner wall of the hub shell 208, and the primary driving body 202 drives the hub shell 208 through the primary pawl 402 when rotating. When the hub shell 208 rotates faster, the teeth in the primary toothed ring 412 can press down the primary pawl 402, and after the pressing force disappears, the primary pawl 402 can automatically reset to be meshed with the primary toothed ring 412 which is elastically and repositionably fixed on the primary driving body 202 again due to the elastic snap ring 502.

Continuing with FIG. 4, the primary pawl 402 has a groove 414 formed in a surface thereof for retaining the snap ring 502. The primary pawl 402 includes an engaging portion 406 engaging with the primary toothed ring 412, and a rotating portion 408 for providing a pivot point for the primary pawl 402, the rotating portion 408 having an arc-shaped surface; the overall structure of the primary pawl 402 is substantially a whistle-like structure, and a groove 414 for fixing the elastic snap ring is arranged between two identical whistle-like structures. When the snap ring 502 is snapped into the groove 410 of the primary pawl 402, the tail of the primary pawl 402 is pressed down, and the primary pawl 402 rotates around the rotating portion 408 due to the pressing force, so that the engaging portion 406 of the pawl is tilted to engage with the primary toothed ring 412 on the inner wall of the hub shell 208.

In order to fix the detent seat 410, a snap ring groove 436 is provided, and the detent is caught by the snap ring groove 436 at the same time, thereby fixing both.

In fig. 4, the hub shell 208 and the primary gear ring 412 on the inner wall are of a split structure. The outer surface of the primary toothed ring 412 is provided with dense mounting teeth 432, and the inner wall of the hub shell 208 is provided with a tooth structure meshed with the mounting teeth 432. The inner surface of the primary toothed ring 412 is provided with drive teeth 434 for engagement with the pawls. When the pawl rotates, the drive tooth 434 drives the toothed ring 412 to further drive the hub to rotate.

The power is directly transmitted from the primary driving body 202 to the hub shell 208 through the primary pawls 402, and the power is directly transmitted with high efficiency. And the use of a single drive body at a primary speed avoids the risk of rotation due to possible connection problems of the drive body with the jaw seat connecting splines, while the single drive body enables the hub shell 208 and the shaft, the hub shell 208 and the primary drive body 202, and the primary drive body 202 and the shaft to be connected by bearings with better sealing performance. And the shear force that the flower-drum axle that its leads to also directly disappears after the claw seat body disappears, and the wear to the axle is littleer. Meanwhile, the problem of large axial length of the automatic speed change is solved. The requirement of the middle-mounted motor on the axial space is met, and therefore a brand-new solution is provided for the physical speed change of the middle-mounted motor. The bicycle is used for a single-arm bicycle, and has the characteristics of attractive appearance, simplicity, convenience, easy maintenance, comfortable riding and good water resistance.

Fig. 5 is a schematic view of the overall structure of the primary drive body 202, which includes the planetary gear set star wheel portion driven by the primary drive body 202 and the secondary drive body 320.

Referring to fig. 3-5, the primary drive body 202 and the secondary drive body 320 are connected by a planetary gear set. A planet carrier 504 is arranged at the end of the primary drive body 202, three planet wheels 506 are arranged on the planet carrier 504, and the planet wheels 506 are engaged with the sun wheel 322 arranged on the hub shaft 204. The secondary driving body 320 is provided with a gear ring 324 meshed with the star wheel 506, when the secondary driving body rotates, the primary driving body 202 drives the star wheel to rotate, and the star wheel 506 drives the gear ring 324 to rotate at an increased speed; the ring gear 324 drives the secondary driving body 320 to integrally rotate.

Fig. 6 to 8 are side views of the secondary driving body 320, and fig. 6 retains the complete structure of the secondary driving body 320. Fig. 7 omits one of the centrifugal weights 428 on the secondary drive body 320 to facilitate a clear view of the clutch plate 424 and torsion spring 702 configuration. Fig. 8 hides the clutch plate 424 and the centrifugal block 428 and the fixed shaft 426 to facilitate visual inspection of the secondary pawl 802 engagement and the secondary drive ring gear 416.

Referring to fig. 6, the secondary driving body 320 drives the hub housing 208 to rotate when the rotation speed reaches a shift value. The secondary drive body 320 includes an eccentric mass 428 that rotates with the ring gear 324. The centrifugal block 428 is fixed on the secondary driving body 320 by a fixing shaft 436. The fixing shaft 436 is fixed to the secondary driving body 320 through a hole 704 provided on the clutch plate 424, and a large stroke space is provided between the edge of the hole on the clutch plate 424 and the fixing shaft 436 for the clutch plate 424 to drive the secondary pawl 600 to engage with the ring of the driving teeth 420. A torsion spring 702 is arranged on the fixed shaft 436 to provide a resetting force for resetting the centrifugal block 428; the centrifugal block 428 is provided with a driving shaft 430 connected with the clutch plate 424, and the driving shaft drives the clutch plate 424 to rotate when the centrifugal block 428 rotates around the fixed shaft 436.

As the rotational speed is gradually increased to the shift value, the centrifugal mass 428 rotates along the fixed shaft 436 thereof and drives the clutch plate 424 to rotate clockwise, and the clutch plate 424 rotates clockwise under the driving action of the centrifugal mass 428 and drives the secondary pawl 600 into engagement with the driving ring gear 420. The gear ring 420 engages with a secondary gear ring 416 arranged inside the hub housing 208 via external gear teeth 422, which in turn drives the hub housing 208 in rotation. It should be noted that the transmission gear ring 420 is not required, and those skilled in the art can omit the transmission gear ring 420 by properly setting the inner diameter of the hub shell 208 so that the secondary gear ring 416 of the inner wall of the hub can directly engage with the secondary pawl 600. One skilled in the art can also properly set the outer diameter of the secondary driving body 320 so that the secondary pawls 600 can directly engage with the inner wall of the hub.

The secondary pawl 600 is fixed to the primary pawl 402 in the same manner as the primary pawl, and is also fixed to the secondary driving body 320 by an elastic snap ring. When the rotation speed of the secondary driving body 320 is reduced to be lower than a gear shifting value, the torsion spring on the fixed shaft 436 of the centrifugal block 428 drives the centrifugal block 428 to reset, the centrifugal block 428 drives the clutch plate 424 to reset, and the clutch plate 424 further drives the secondary pawl reset 600. After the secondary pawls 600 are reset, the transmission of the driving force between the secondary driving body 430 and the drum housing 208 is cut off, and the drum housing 208 is directly driven by the primary driving body 202.

Referring to fig. 7 and 8, the clutch plate includes a pawl slot for receiving the secondary pawl 600, the pawl slot 706 includes a first receiving portion 708 and a second receiving portion 710, and the second receiving portion 710 is located at the radial outer side of the first receiving portion 708; at low rotational speeds, the clutch plate 424 is not rotated, and the engagement portion 602 of the secondary pawl 600 is received in the first receiving portion 708. When the clutch plate 424 is driven to rotate by the centrifugal block 428, the first receiving portion 708 rotates forward relative to the engaging portion of the secondary pawl 600, the first receiving portion 708 does not have a limiting effect on the secondary pawl 600, the secondary pawl 600 enters the second receiving portion 710 from the first receiving portion 708 due to the elastic snap ring 502, and the engaging portion 602 engages with the driving teeth 422 of the driving gear ring 420 after entering the second receiving portion 710. The transmission gear ring 420 is provided with a pawl slot 802 for engaging with the pawl, and the driving force is transmitted to the transmission gear ring 420 through the pawl slot 802 and then transmitted to the hub housing 208.

The pawl slot 802 is smoothly cambered and the forward edge of the engagement portion on the secondary pawl 602 is smooth so that it smoothly compresses the secondary pawl 602 from the second receiving portion 710 back into the first receiving portion 708 for disengagement from the drive ring gear when the clutch plate 424 is reset.

Claims

1. An internal shift hub, comprising:

a shaft;

2. The internal shift hub as set forth in claim 1, wherein said primary pawl is resiliently resettable secured to said primary drive body.

3. The internal shift hub as set forth in claim 2, wherein said primary pawl is secured to said primary drive body by a resilient snap ring; the surface of the primary driver is provided with a concave part for accommodating the primary pawl, and the surface of the primary pawl is provided with a groove for fixing the elastic snap ring; and the primary driving surface is provided with a groove for fixing the elastic snap ring.

4. The internal shift hub as set forth in claim 3, wherein said primary pawl includes an engaging portion engaging with said primary toothed ring, and a rotating portion for providing a rotational fulcrum of said primary pawl, said rotating portion having an arc-shaped surface; a cavity for accommodating and allowing the rotating part to rotate therein is arranged in the concave part of the surface of the driving body.

5. The internal variable speed hub as claimed in claim 1, further comprising a secondary drive body, wherein the primary drive body and the secondary drive body are connected by a planetary gear set; the primary driving body drives the secondary driving body to rotate at an increased speed through the planetary gear set.

6. The internal shift hub as set forth in claim 5, wherein said shaft is provided with a sun gear of a planetary gear set; the primary driving body is provided with a star wheel meshed with the sun wheel; the secondary driving body is provided with a gear ring meshed with the star wheel; when the star wheel rotates, the first-stage driving body drives the star wheel to rotate, and the star wheel drives the gear ring to rotate at an increased speed; and the gear ring drives the secondary driving body to integrally rotate.

7. The internal shift hub as set forth in claim 6, wherein said secondary drive body includes a centrifugal mass that rotates with said ring gear, a clutch plate driven by said centrifugal mass, and a secondary pawl; when the rotating speed is increased, the centrifugal block rotates along the fixed shaft of the centrifugal block and drives the clutch plate; the clutch plate rotates along with the centrifugal block and drives the secondary pawl to be meshed with a secondary toothed ring on the inner wall of the shell; when the rotating speed is reduced, the centrifugal block drive, the clutch plate and the secondary pawl reset respectively.

8. The internal shift hub as claimed in claim 7, wherein the clutch plate includes a pawl slot for receiving the secondary pawl, the pawl slot includes a first receiving portion and a second receiving portion that are in communication, and the second receiving portion is radially outside the first receiving portion; the clutch plate is driven by the centrifugal block, and the secondary pawl enters the second accommodating part from the first accommodating part; when the clutch plate is reset, the pawl enters the first accommodating part from the second accommodating part.

9. The internal variable speed hub as claimed in claim 7, wherein the centrifugal mass is fixed to the secondary driving body by a fixed shaft; the fixed shaft is provided with a torsion spring for providing a reset force for resetting the centrifugal block; the centrifugal block is provided with a driving shaft connected with the clutch plate, and the driving shaft drives the clutch plate to rotate when the centrifugal block rotates around the fixed shaft.

10. The internal shift hub as set forth in claim 7, wherein a drive ring gear is disposed within said hub housing for engaging said secondary pawl, said drive ring gear engaging said secondary ring gear.