CN108974242B - Variable speed hub centrifugal clutch assembly and automatic internal three-speed hub - Google Patents
Variable speed hub centrifugal clutch assembly and automatic internal three-speed hub Download PDFInfo
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- CN108974242B CN108974242B CN201811063893.9A CN201811063893A CN108974242B CN 108974242 B CN108974242 B CN 108974242B CN 201811063893 A CN201811063893 A CN 201811063893A CN 108974242 B CN108974242 B CN 108974242B
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- gear set
- centrifugal
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- 239000000969 carrier Substances 0.000 description 4
- 230000013011 mating Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 238000009434 installation Methods 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
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- 230000009286 beneficial effect Effects 0.000 description 1
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
- B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
- B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
- B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
- B62M11/16—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears built in, or adjacent to, the ground-wheel hub
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
- B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
- B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
- B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
- B62M11/18—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears with a plurality of planetary gear units
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Abstract
The invention relates to a variable speed hub centrifugal clutch assembly and an automatic internal three-speed hub, which comprises a hub shaft for supporting and installing; a hub shell as a power output; the first planetary gear set, the second planetary gear set and the direct drive part are arranged on the hub shaft; the first planet carrier of the first planetary gear set drives the second planet carrier of the second planetary gear set, and the second planet carrier drives the direct drive part; the gear ring of the first planetary gear set is provided with a first centrifugal clutch which is combined above a first pedal frequency, and the second planetary gear set is provided with a second centrifugal clutch which is combined above a second pedal frequency; the first centrifugal clutch or the second centrifugal clutch comprises a centrifugal block, a clutch plate and a pawl, wherein the centrifugal block drives the clutch plate to radially rotate when the clutch plate is combined, and the clutch plate rotates the pawl to be meshed with a driving part of the hub shell; the flower-drum structure simplifies the existing internal three-speed flower-drum, so that the flower-drum structure is more reasonable and automatic in speed change.
Description
Technical Field
The invention belongs to the field of bicycles, and particularly relates to an improvement on a variable speed hub.
Background
The existing manual internal three-speed variable speed hub system comprises an internal three-speed hub, a speed change line, a speed change push rod and a speed change rotating handle. It has at least the following problems:
the gear cannot be automatically switched, and the speed is regulated manually according to the pedal frequency. The speed-regulating rotating handle occupies the holding space of the handle, and the exposed speed-changing wire and the speed-regulating rotating handle influence the appearance of the whole vehicle.
Parts such as a speed change push rod matched with the speed change line need to be delayed in the hub, so that the layout of internal components is unreasonable, the whole vehicle assembly is complex, and the requirement on the whole vehicle installation precision is high.
The whole system is too complicated, and the speed change push rod and the speed change wire are easy to damage due to leakage, and the speed change wire is easy to age, so that the function is invalid, and periodic maintenance is needed.
The aim of the present invention is therefore to propose a new automatic three-speed drum to eliminate the above drawbacks.
Disclosure of Invention
In order to solve the technical problems, the invention is provided with the centrally-mounted planet carrier, the combination of different pedaling frequencies is realized through centrifugal clutch on the toothed rings of the first planetary gear set and the second planetary gear set, and the toothed rings of the first planetary gear set and the second planetary gear set drive the hub shell to output different speeds.
More specifically, the automatic inner three-speed hub comprises:
a hub shaft for supporting and mounting;
a hub shell as a power output;
the first planetary gear set, the second planetary gear set and the direct drive part are arranged on the hub shaft;
the first planet carrier of the first planetary gear set drives the second planet carrier of the second planetary gear set, and the second planet carrier drives the direct drive part;
the gear ring of the first planetary gear set is provided with a first centrifugal clutch which is combined above a first pedal frequency, and the gear ring of the second planetary gear set is provided with a second centrifugal clutch which is combined above a second pedal frequency;
the first centrifugal clutch or the second centrifugal clutch comprises a centrifugal block, a clutch plate and a pawl, the centrifugal block drives the clutch plate to radially rotate when the clutch plate is combined, and the clutch plate rotates to release the pawl to be meshed with the driving part of the hub shell.
In a preferred embodiment, the centrifugal block is arranged on a mounting shaft on the toothed ring, and the centrifugal block drives the clutch plate to radially rotate when rotating around the mounting shaft.
In a preferred embodiment, the centrifugal block is connected to the clutch plate by a drive; the centrifugal block is connected with a reset piece, and the reset piece drives the centrifugal block and the clutch plate to reversely rotate when the clutch is separated.
In a preferred embodiment, the clutch plate includes a pawl receiving slot in which the pawl is partially received; the pawl receiving groove releases the pawl from the initial position to a position engaged with the drive portion of the drum housing upon clutch engagement.
In a preferred embodiment, the pawl comprises an arc-shaped supporting part, the back of the arc-shaped supporting part is provided with a spring groove, and an axial fixing spring passes through the spring groove to axially fix the pawl on the toothed ring; the spring presses the back of the arc-shaped supporting part so that the pawl always tends to be far away from the pawl accommodating groove; when the clutch is combined, the clutch plate rotates to a disengaging position where the pawl can be disengaged from the accommodating groove, and the pawl pops up from an initial position under the action of the spring and is meshed with the driving part of the hub shell.
In a preferred embodiment, the hub driving part comprises a ratchet ring and a fixed toothed ring meshed with the outer teeth of the ratchet ring, wherein the fixed toothed ring is fixedly connected with the hub or integrally arranged with the hub, and the ratchet teeth of the ratchet ring are meshed with the pawl when the ratchet ring is combined with the clutch.
In a preferred embodiment, the reset piece is a torsion spring arranged on the installation shaft of the centrifugal block, and the torsion spring of the first clutch assembly drives the centrifugal block to reversely rotate around the installation shaft when the first centrifugal clutch is separated and the pedal frequency is lower than the first pedal frequency; when the second centrifugal clutch is separated, the pedal frequency is lower than the pedal frequency of the torsion spring of the second clutch assembly, and the torsion spring drives the centrifugal block to reversely rotate around the mounting shaft.
In a preferred embodiment, the driving part is a driving rod matched with the clutch plate, an opening matched with the driving rod is arranged on the clutch plate, and the driving rod part is accommodated in the opening and drives the clutch plate to rotate through the opening.
In a preferred embodiment, the direct drive portion is provided with a pawl which directly engages the drive portion of the drum housing.
In a preferred embodiment, the first tread frequency is greater than the second tread frequency; when the pedal frequency is smaller than the second pedal frequency, the direct drive part drives the hub shell, and the first centrifugal clutch and the second centrifugal clutch idle; when the pedal frequency is larger than the second pedal frequency and smaller than the first pedal frequency, the second centrifugal clutch is combined, and the direct drive part and the first centrifugal clutch idle; when the pedal frequency is larger than the first pedal frequency, the first centrifugal clutch and the second centrifugal clutch idle.
The invention also provides a speed-changing hub centrifugal clutch assembly based on the same technical principle, which comprises the following components:
the power input part is used for installing the centrifugal block, the clutch plate and the pawl;
the ratchet ring is used for outputting power to the hub shell when being meshed with the pawl;
when the clutch is combined, the centrifugal block drives the clutch plate to radially rotate to release the pawl to be meshed with the ratchet ring;
when the clutch is disengaged, the disengaging part of the ratchet ring rotates to force the pawl to be forcibly disengaged from the ratchet ring and locked by the clutch plate.
In a preferred embodiment, the power input is a ring gear of a planetary gear set.
In a preferred embodiment, the separating portion of the ratchet ring is a protruding portion protruding inwards, wherein the protruding portion is arranged inside the ratchet ring, the ratchet ring rotates with the hub shell in an inertial mode during clutch separation, and the protruding portion pushes the pawl away from the ratchet ring, so that the ratchet ring and the ratchet ring are forcedly separated and locked by the accommodating groove on the clutch plate.
As a further improvement, the present invention also provides another automatic inner three-speed hub comprising:
a hub shaft for supporting and mounting;
a hub shell as a power output;
a first planetary gear set and a second planetary gear set mounted on the hub axle;
the first planetary gear set and the second planetary gear set are arranged in a mirror image mode, and a first planet carrier of the first planetary gear set drives a second planet carrier of the second planetary gear set;
the gear ring of the first planetary gear set is provided with a first centrifugal clutch which is combined above a first pedal frequency, and the second planetary gear set is provided with a second centrifugal clutch which is combined above a second pedal frequency;
the first centrifugal clutch or the second centrifugal clutch comprises a centrifugal block, a clutch plate and a pawl, the centrifugal block drives the clutch plate to radially rotate when the clutch plate is combined, and the clutch plate rotates to release the pawl to be meshed with the driving part of the hub shell.
In the preferred embodiment, power is transmitted through a sleeve connection provided on the hub axle.
In a preferred embodiment, the planet carrier of the second planetary gear set has pawls thereon for directly driving the hub shell.
The invention has the beneficial technical effects that the automatic internal three-speed variable speed hub of the bicycle eliminates the finger shifting system (a speed change line, a speed change push rod and a speed change rotary handle) of the original internal three-speed variable speed hub, and the appearance of the bicycle can be further improved.
The structure of parts such as a speed change push rod is eliminated, the whole vehicle assembly is simpler, the stability of the back shaft rotary motion is improved, and the reliability and the safety of use are improved.
Automatic interior three-speed is as interior speed change system, and speed change gear installs and need not the variable speed line in flower-drum shell inside, avoids exposing in the external world through multilayer sealed protection, consequently all can't get into by rainwater, dust, oil dirt etc. also avoided the insolation of sun and the erosion of wind and rain, so need not periodic maintenance, realized advantages such as maintenance-free, accurate, durable, light and handy, reached convenient to use pleasing to the eye effect.
The first centrifugal clutch and the first centrifugal clutch are automatically combined or separated at the first pedal frequency and the critical point of the first pedal frequency, and the speed change is continuous, so that a user does not need any pause.
Drawings
FIG. 1 is a schematic diagram of a cross-sectional structure of an automatic inner three-speed hub.
Fig. 2 is a schematic cross-sectional structure of an automatic inner three-speed drum, wherein the shell of the drum is omitted.
Fig. 3 is a schematic top view of the centrifugal clutch.
Fig. 4 is a schematic top view of the centrifugal clutch plate of fig. 3.
Fig. 5 is a schematic top view of fig. 3 with the centrifugal mass and clutch plates omitted.
Fig. 6 is a schematic cross-sectional view of the centrifugal clutch.
Fig. 7 is a schematic diagram of a drum perspective structure, and shows a 1/4 section.
Fig. 8 is a schematic cross-sectional view of a three-speed hub in example 2.
Detailed Description
Example 1
Referring to the automatic inner three-speed hub 100 shown in fig. 1 to 8, the inner three-speed hub comprises a two-stage planetary gear set, wherein the central planetary carriers 11 and 21 are used as driving components, centrifugal clutches are arranged on the tooth rings 13 and 23 of the planetary gear set, and the clutches are respectively engaged under different pedaling frequencies of a bicycle rider so that the hub shell as an output member obtains different rotating speeds, and the whole process is automatic due to the existence of the centrifugal clutches.
The automatic inner three-speed hub comprises:
a hub axle 51 for supporting and mounting; a hub casing 61 as a power output; a first planetary gear set 1, a second planetary gear set 2 and a direct drive section 3 mounted on the hub axle 51; the first carrier 11 of the first planetary gear set 1 drives the second carrier 21 of the second planetary gear set, which drives the direct drive section 3; the gear ring 13 of the first planetary gear set 1 is provided with a first centrifugal clutch which is combined above a first pedal frequency, and the second planetary gear set 2 is provided with a second centrifugal clutch which is combined above a second pedal frequency; the first or second centrifugal clutch comprises centrifugal blocks 19, 29, clutch plates 17, 27 and pawls 15, 25, when the centrifugal blocks are combined, the centrifugal blocks drive the clutch plates 17, 27 to radially rotate, and the rotation of the clutch plates 17, 27 is meshed with the locking release pawls 15, 25 and the driving parts 16, 18, 26, 28 of the flower drum shell.
The hub axle 51 is used as a mounting axle of a planetary gear set and a mounting axle of a bicycle wheel, and is fixed on a front fork or a rear fork of the bicycle through fixing nuts 52 or quick-release devices on two sides of the mounting axle 51.
The sun gears 10, 20 of the first planetary gear set 1, the second planetary gear set 2 are mounted on the hub axle 51 or are integrally arranged with the hub axle 51, and the sun gear 10 of the first planetary gear set 1 is fixedly mounted with the hub axle 51 in the invention. The sun gears 10, 20 are fixed on the hub axle and do not rotate during the rotation of the planetary gears 101, 201.
The first planetary carrier 11 includes a flywheel mounting portion 43 and a seal portion 111. The flywheel 41 is provided with a raceway 431 in the mounting portion 43, and the raceway 431 is used for partially accommodating the ball 113 provided between the ball 42 and the carrier 11, and the ball 42 serves to axially fix the carrier 11 and also to axially fix the spline housing 61. The flywheel attachment portion 43 is connected to the flywheel on the outer peripheral side thereof, and the riding force is transmitted to the first carrier 11 through the flywheel 41.
The sealing part 111 extends in the vertical direction and is surrounded by an extending part 115 in the vertical direction of the hub shell 61, a raceway is arranged at the edge of the sealing part, a raceway ring 116 is arranged at the rightmost side of the hub shell, the raceway ring 116 and the raceway of the sealing part jointly accommodate a rolling ball 114, and the hub shell is supported by the first planetary gear set 1 through the rolling ball 114.
A star wheel shaft 102 (see fig. 7) is mounted on the inner side of the seal portion 11, and a ring gear 13 of the first planetary gear set is formed in a tower shape, and includes a meshing portion 12 connected to the star wheel 101, and a clutch mounting portion 14 for mounting a first centrifugal clutch, the centrifugal clutch being connected to the clutch mounting portion 14 radially outside the drum shell driving portions 16, 18 when the centrifugal clutch is engaged. It should be noted that the ring gear 13 of the first planetary gear set 1 is not directly mounted on the hub axle 51, but is sleeved on the planet carrier 21 of the second planetary gear set through the housing cavity 200 of the second planet carrier on the radial inner side of the centrifugal clutch mounting portion 14, the housing cavity 200 of the ring gear and the outer wall of the planet carrier are cylindrical, and the ring gear 13 of the first planetary gear set 1 can rotate around the second planet carrier 21 as an axle.
The carrier 21 of the second planetary gear set 2 is mounted on the hub axle 51, and the main body portion of the carrier is received in the receiving cavity 200 of the ring gear of the first planetary gear set. The planetary gear set has a connection 211, which connection 211 is connected to the carrier 11 of the first planetary gear set. When the first planetary gear set 1 rotates, the carrier 21 of the second planetary gear set is driven to rotate through the connection portion 211.
The toothed ring 23 of the second planetary gear set is in the shape of a pagoda, and comprises a meshing part 22 connected with the star wheel and a clutch mounting part 24 for mounting a second centrifugal clutch, wherein the centrifugal clutch is connected with driving parts 26 and 28 of the hub shell on the radial outer side of the clutch mounting part 24 when being combined. The toothed ring 23 of the second planetary gear set is sleeved on the direct-drive part 31 through a containing cavity 300 arranged on the radial inner side of the centrifugal clutch mounting part 24, the right end part of the direct-drive part is connected with the planet carrier 21 of the second planetary gear set, the containing cavity 300 and the outer wall of the direct-drive part are cylindrical, and the toothed ring 23 of the second planetary gear set can rotate by taking the direct-drive part 31 as a shaft.
The planet carrier 21 of the second planetary gear set drives the direct drive part 31 to synchronously rotate, and the left side of the direct drive part is provided with a driving wheel 32, and the driving wheel 32 is radially outwards extended and meshed with a driving part 34 of the hub shell through a pawl 33 arranged on the driving wheel 32.
The carrier 11 of the first planetary gear set 1 is driven by the flywheel 41 during riding, and the carrier 21 and the direct drive portion 31 of the second planetary gear set 2 rotate in synchronization with the carrier 11 of the first planetary gear set. The three components remain rotated in synchronization regardless of the rider's pedaling frequency.
And the first tooth ring 13 and the second tooth ring 23 of the first planetary gear set 1 and the second planetary gear set 2 are different in the corresponding gear ratio, so that the rotation speeds of the different tooth rings are also different under the same pedaling frequency. Therefore, the centrifugal clutch is combined under different pedal frequencies, and the aim of speed change is fulfilled.
The critical rotational speed at which the centrifugal clutch is engaged is fixed for a gear-ratio-determining planetary gear set, and therefore the critical pedal frequency of the centrifugal clutch is also determined for a gear-ratio-determining tooth disc and flywheel combination. The shift threshold pedal frequency can be adjusted by those skilled in the art by adjusting the gear ratio of the planetary gear set or the gear ratio of the dog plate and flywheel as desired.
The gear of the internal three-speed automatic transmission hub is divided into three gears, namely a low gear, a middle gear and a high gear, the rotation speeds output by the corresponding hub shells of the gear are respectively low, medium and high, the critical pedal frequency corresponding to the three rotation speeds is second pedal frequency and first pedal frequency, the hub is lower than the second pedal frequency and is in a low-gear low-speed state, the hub is in a medium-gear medium-speed state with the second pedal frequency being greater than or equal to the second pedal frequency and smaller than the first pedal frequency, and the hub is in a high-gear high-speed state with the first pedal frequency.
The automatic upshift process of the hub is different according to different gears, and the riding power transmission paths are also different:
in the low range, the riding power with the riding frequency smaller than the second riding frequency is input from the flywheel 41, transmitted to the planet carrier 21 of the second planet gear through the planet carrier 11 of the first planet gear, transmitted to the direct drive part 31, and finally reaches the hub shell 61. In order to more clearly show the transmission path of the driving force, referring to the path indicated by the arrow shown in fig. 2, a- > B- > C- > D- > E- > F- > H, the driving force is transmitted from the carrier 11 of the first planetary gear set to the second planetary gear set 2 via the connection 211 of the carrier 21 of the second planetary gear set, said first carrier 11 and second carrier 21 connection 211 being transmitted by a splined connection. At this time, the pedal frequency is lower than the second pedal frequency, and therefore both the first centrifugal clutch and the second centrifugal clutch are in a disengaged state, and the first ring gear 11 of the first planetary gear set 1 and the second ring gear 21 of the second planetary gear set 2 are in a no-load idling state, that is, the first and second centrifugal clutches are in a disengaged idling state. The power is transmitted from the second planetary gear carrier to the driving wheel 32 at the right end of the direct-drive part through the path I- > J- > L- > M, and a pawl 33 (the driving part 34 and the pawl 33 are described in detail below) engaged with the driving part 34 of the drum shell is provided on the driving wheel 32, and the riding power is transmitted to the drum shell 61 through the pawl 33 and the driving part 34. Since the first centrifugal clutch and the second centrifugal clutch are not combined during the entire low gear transmission, the rotational speed of the output of the hub shell 61 is the same as the rotational speed of the input of the flywheel 41.
In the middle gear, the pedal frequency of a rider is larger than that of the second pedal frequency and smaller than that of the first pedal frequency, riding power is input from a flywheel, is transmitted to the planet carrier 21 of the second planetary gear through the planet carrier 11 of the first planetary gear, finally reaches the shell 61 through centrifugal clutch of the second planetary gear set, and the power transmission path is A- > B- > C- > D- > E- > F- > H- > I- > J- > K. Since the riding frequency is greater than the second frequency and less than the first frequency, the second centrifugal clutch is engaged and the pawls 25 on the second centrifugal clutch are engaged with the drum shell drive portions 26, 28. The toothed ring 23 of the second planetary gear set 2 drives the hub shell 61 through the pawls 25, and the toothed rings 23 of the hub shell 61 and the second planetary gear set synchronously rotate at a rotational speed greater than that of the direct drive portion 31 and the first and second planetary carriers 11, 21. At this time, the pawls 33 on the driving wheel 32 of the direct-drive section 31 are disengaged from the drum shell driving section 34, and the direct-drive section 31 is in an idle state. The corresponding pedal frequency is smaller than the first pedal frequency, so that the first centrifugal clutch is in a separated state, and the toothed ring 11 of the first planetary gear set 1 idles, i.e., the first centrifugal clutch is in a separated idle state.
In the high gear, the riding power is input from the flywheel 41 and transmitted to the first planet gear frame 11, and is transmitted to the hub shell 62 through the first centrifugal clutch, and the power transmission path is A- > B- > C- > D- > E- > F- > G. Since the pedal frequency is greater than the first pedal frequency, the first centrifugal clutch on the first ring gear 13 of the first planetary gear set 1 is engaged, and the pawls 15 on the first centrifugal clutch are engaged with the drum shell driving portions 16, 18. The toothed ring 13 on the first planetary gear drives the hub shell 61 through the pawl 15, and the hub shell 61 rotates synchronously with the toothed ring 13 of the first planetary gear at a rotational speed greater than that of the toothed ring 23 and the direct drive part 31 of the second planetary gear. At this time, the pawls 33 on the driving wheel 32 of the direct-drive portion 31 are disengaged from the drum housing 61, and the pawls 15 of the second centrifugal clutch are also disengaged from the drum housing 61, and the direct-drive portion and the second planetary gear set are both in an idling state.
In the automatic shift-down process of the hub, the shift-up action is opposite, when the pedal frequency is reduced to be lower than the first pedal frequency and higher than the second pedal frequency, the first centrifugal clutch is separated, and the second centrifugal clutch is combined to be shifted down to the middle gear, and at the moment, the toothed ring 13 and the direct drive part 31 of the first planetary gear set 1 are in an idle state. When the pedal frequency is lowered below the second pedal frequency, the engagement of the second centrifugal clutch release direct-drive portion 31 with the drum housing is lowered to the low gear, and at this time, the ring gear 13 of the first planetary gear set 1 and the ring gear 23 of the second planetary gear set 2 are both in the idling state. The first centrifugally clutched pawl 15 is disengaged from the driving parts 16, 18 of the drum from the high gear down to the medium gear, and the second centrifugally clutched pawl 25 is disengaged from the driving parts 26, 28 of the drum from the medium gear down to the low gear.
The working principles of the first centrifugal clutch and the second centrifugal clutch are completely the same, the difference between the first centrifugal clutch and the second centrifugal clutch is that critical pedal frequencies of the first centrifugal clutch and the second centrifugal clutch are different, and different pedal levels correspond to different gear positions of the automatic transmission hub. Taking the first centrifugal clutch as an example, the working principle of the centrifugal clutch is explained.
The first centrifugal clutch comprises a centrifugal block 19, a clutch plate 17 and a pawl 15, all of which are arranged on the toothed ring 13 of the first planetary gear set. The diameter of the star wheel engaging part 12 of the toothed ring 13 is larger than that of the clutch mounting part 14, and a space for accommodating the pawl 15, the clutch plate 17 and the centrifugal block 19 is formed in a ring shape on the radial outer side of the clutch mounting part 14.
The centrifugal block has an arc-shaped block structure, the mounting shaft 191 is sleeved at the tail of the arc-shaped block structure, the centrifugal block mounting shaft 191 is directly arranged on the toothed ring 13, the centrifugal block 19 is arranged on the mounting shaft 191, and the centrifugal block 19 rotates around the mounting shaft 191 when the clutch is combined or separated to drive the clutch plate to radially rotate, and in fig. 3, the centrifugal block and the toothed ring 13 both rotate anticlockwise.
The rotation of the centrifugal block 19 around the mounting shaft 191 is caused by the centrifugal effect generated by the rotation of the toothed ring 13, meanwhile, the toothed ring 13 is also used as a power input part of the clutch device, and the toothed ring 13 and the driven hub shell 61 synchronously rotate when in clutch combination, and obviously, the power input part can also be a rotating part of a non-planetary gear, so long as the rotating part can rotate to cause the centrifugal block 19 to generate an effective centrifugal effect.
The centrifugal block 19 is connected with the clutch plate 17 through a driving part 192; the driving part 192 is a driving rod 192 disposed on one side of the centrifugal block mounting shaft 191 and coupled to the clutch plate 17, one end of the driving rod 192 is sleeved in the driving rod mounting hole of the centrifugal block 19, the other end of the driving rod 192 abuts against the coupled opening 170 disposed on the clutch plate 17, and a part of the driving rod 192 is accommodated in the opening 170. The drive may also be in other forms of drive than a shaft, for example using a mechanical structure such as hooks, gears, ratchets, push rods, levers, etc. instead of the drive rod.
When the pedal frequency gradually rises to the first pedal frequency, the centrifugal clutch rotates around the mounting shaft 191 due to the centrifugal effect, the driving rod 192 rotates around the centrifugal block mounting shaft 191 along with the centrifugal block 19, and the driving shaft 191 drives the clutch plate 17 to radially rotate through the accommodating groove 170 on the clutch plate 17.
The clutch plate 17 includes a pawl receiving recess 170 including a lower edge 172 and an upper edge 171, the pawl 15 being partially received in the pawl receiving recess 170; the clutch plate 17 rotates to a disengaged position in which the pawls can be disengaged from the receiving grooves 170, and the pawls are ejected from the initial position by the action of the spring and engaged with the driving portion of the drum housing. In the engaged position, the portion of the pawl 15 not received by the pawl receiving recess 170 engages the drive portion 16 of the drum housing when engaged.
The pawl comprises an arc-shaped supporting part 153, the back of the arc-shaped supporting part is provided with a spring groove 154, and an axial fixing spring 151 passes through the spring groove to axially fix the pawl on the toothed ring 14; the spring 15 urges the back 154 of the arcuate support such that the pawl 15 always tends to move away from the pawl receiving recess 170; therefore, once the accommodating groove 170 rotates to the disengaged position, the pawl 15 is disengaged from the accommodating groove 170, and is engaged with the driving part after rotating by a certain angle with the arc-shaped supporting part as a fulcrum under the action of the spring.
The toothed ring includes a pawl mounting location 141 in which the initial position of the pawl is maintained during disengagement by the receiving slot 170 in the clutch plate. A plurality of pawls 15 are provided on the toothed ring 13 at positions symmetrical about the center. The pawl 15 mounting position 141 is a concave structure formed on the toothed ring, the volume of the concave structure is slightly larger than that of the pawl 15, and the clutch plate 17 rotates to be engaged with the driving part of the hub shell 61.
The hub drive includes a ratchet ring 16 and a fixed gear ring 18 engaged with the ratchet ring outer teeth. The fixed gear ring 18 is fixedly connected with or integrally provided with the hub shell 61. The ratchet ring 16 includes a plurality of sets of ratchet teeth, the ratchet teeth include a pawl receiving portion 160 and a protrusion 163, the front end of the pawl receiving portion 160 is a mating groove 162 that abuts against the front end 152 of the pawl, the pawl transmits riding force to the hub shell through the mating groove 162 when engaged, and the protrusion 163 blocks the pawl 15 from being disengaged from the mating groove.
The first centrifugal clutch is engaged when the pedal frequency gradually increases from the second pedal frequency to the first pedal frequency, and the rotational speed of the hub shell 61 becomes high, which is higher than the rotational speed of the second carrier 21; the ratchet ring 26 on the second planetary gear set 2 rotates synchronously with the hub shell 61, and the pawls 25 are disengaged from the engaging grooves 162, so that the output load of the second planetary gear set disappears into an idling state.
When the tread frequency gradually decreases from higher than the first tread frequency to the second tread frequency, at this time, the rotational speed of the hub shell 61 is higher than the rotational speed of the ring gear 11 of the first planetary gear set 1 due to inertia, the ratchet ring 16 overruns the pawl 15, the boss 163 located behind the pawl 15 overruns the pawl 15, and pushes the pawl 15 out of the receiving groove 160 back to the mounting position 141, and at the same time, the restoring force of the centrifugal block 19 drives the centrifugal block and the clutch plate 17 to reversely restore and rotate, the pawl 15 again enters the receiving groove 170 on the clutch plate, and at this time, the pawl is locked back to the mounting position because the receiving groove 170 has returned to the original position. And at this time a second tread frequency is reached, the pawls 25 on the second centrifugal clutch engage with the pawls 25 on said second planetary gear set 2 and with the mating grooves on the ratchet ring 26, completing the step of going from high to medium speed.
It should be noted that the boss 163 also serves as a stop for the pawl to prevent the pawl from exiting the engagement slot 162 and also serves as a disengaging portion for disengaging the pawl, and that a separate disengaging portion may be provided in the art to engage the pawl with the ratchet ring as it overruns the pawl, including but not limited to, a push rod, ball, hook, spring, etc.
When the user suddenly stops stepping, i.e., the stepping frequency is directly reduced to zero, the ring gear 11 of the first planetary gear set 1 and the ring gear 21 of the second planetary gear set 2 stop rotating, so that the pawls 15 on the first planetary gear and the pawls 25 on the second planetary gear are disengaged from the receiving grooves and pushed back to the mounting position 141 by the protruding portions 163, and similarly, the pawls 15 are locked again by the mounting grooves, thereby completing the direct shift from the high gear to the low gear.
The centrifugal block 19 is connected with a reset piece, and the centrifugal block 19 is always subjected to reset force. The return member is a torsion spring arranged on the mounting shaft of the centrifugal block, although any other known return means may be used instead of the torsion spring by a person skilled in the art.
Example two
The working principle of the centrifugal clutch of the embodiment is identical to that of the centrifugal clutch of the embodiment. It includes three gears: the planetary gear set comprises a low gear, a middle gear and a high gear, wherein the planetary carrier 21 of the second planetary gear set drives the shell 61 to rotate through the pawl 33 in the low gear, the toothed rings of the first centrifugal clutch and the second centrifugal clutch idle, and the power transmission path is A- > B- > C- > D- > F- > G- > I- > J.
In the middle gear, the gear rings of the second direct drive part and the first planetary gear set idle, and the power transmission path is A- > B- > C- > D- > F- > G- > H.
In a high gear, the toothed ring and the direct drive part of the second planetary gear set are in an idle state, and the power transmission path is A- > B- > C- > D- > E.
The present embodiment differs from the first embodiment in that the first planetary gear set 1 of the first embodiment is fitted over the carrier 21 of the second planetary gear set, and in order to ensure that the strength and the size of the gear ratio of the carrier 21 of the second planetary gear set 2 cannot be too small, the diameter of the first planetary gear set 1 is large, and the maximum diameter of the outside of the hub itself 100 is large.
In this embodiment, the first planetary gear set 1 and the second planetary gear set 2 are arranged in mirror image, so that there is no sleeving relationship between the gear rings 13 and 23 of the first planetary gear set 1 and the second planetary gear set 2 and the planet carriers 11 and 21, and the volume of the first planetary gear set 1 can be effectively reduced, thereby reducing the volume of the hub. In a preferred embodiment, the diameters of the first and second planetary gear sets 1 and 2 are set to be the same so that the outer appearance of the hub is cylindrical and has a smaller diameter.
Meanwhile, since the function of mirroring the direct drive portion 31 of the first planetary gear set is replaced by the carrier 21 of the second planetary gear set, the structure is simplified compared with the first embodiment, and the number of parts is reduced so that the structure is more reasonable.
More specifically, the planet carrier 21 of the first planetary gear set and the planet carrier 11 of the second planetary gear set are connected through a transmission sleeve 71, the radial inner side of the clutch mounting part 14 of the first planetary gear set is sleeved on the right end part of the transmission sleeve, and the mirror image inner side of the clutch mounting part 24 of the second planetary gear set is sleeved on the left end part of the transmission sleeve.
The sleeve 71 is fixedly connected with the carriers 11, 21 of the first and second planetary gear sets, the leftmost side of the carrier 21 of the second planetary gear set forms a driving wheel 232 instead of the driving wheel 32 on the direct driving part in the first embodiment, the pawl 233 is mounted on the driving wheel 232, the driving part 234 is mounted on the hub shell, and the working principles of the driving wheel 232, the driving part 234 and the pawl 233 are the same as those of the first embodiment, and are not repeated.
In summary, the invention uses centrifugal clutch to replace, the clutch push rod system and the speed change rotating handle simplify the existing hub speed change system, so that the hub structure is more reasonable, and meanwhile, the hub speed change process is completely automatic without manual intervention, thereby having better riding experience.
Claims (10)
1. An automatic inner three-speed hub, comprising:
a hub shaft for supporting and mounting;
a hub shell as a power output;
the first planetary gear set, the second planetary gear set and the direct drive part are arranged on the hub shaft;
the first planet carrier of the first planetary gear set drives the second planet carrier of the second planetary gear set, and the second planet carrier drives the direct drive part;
the gear ring of the first planetary gear set is provided with a first centrifugal clutch which is combined above a first pedal frequency, and the gear ring of the second planetary gear set is provided with a second centrifugal clutch which is combined above a second pedal frequency;
the first centrifugal clutch and the second centrifugal clutch comprise centrifugal blocks, clutch plates and pawls, the centrifugal blocks drive the clutch plates to radially rotate when the clutch plates are combined, and the clutch plates rotate to release the pawls to be meshed with a driving part of the hub shell;
wherein the clutch plate comprises a pawl receiving slot in which the pawl is partially received and locked;
the clutch plate rotates to a disengaging position where the pawl can be disengaged from the accommodating groove during gear up, and the pawl pops up from an initial position under the action of a spring and is meshed with the driving part of the hub shell; in the engagement position, the part of the pawl which is not accommodated by the pawl accommodating groove is engaged with the driving part of the hub shell when the pawl is combined in a clutch mode;
during the gear-down, the clutch plate reversely resets to rotate the pawl to enter the accommodating groove on the clutch plate again, the accommodating groove returns to the initial position, and the pawl is locked again.
2. The automatic inner three-speed hub according to claim 1, wherein said centrifugal block is disposed on a mounting shaft on said toothed ring, and wherein said centrifugal block rotates about said mounting shaft to radially rotate said clutch plate.
3. The automatic inner three-speed hub according to claim 2, wherein said centrifugal mass is connected to said clutch plate by a drive portion; the centrifugal block is connected with a reset piece, and the reset piece drives the centrifugal block and the clutch plate to reversely rotate when the clutch is separated.
4. The automatic inside three speed hub according to claim 3, wherein said clutch plate includes a pawl receiving slot, said pawl being partially received in said pawl receiving slot; the pawl receiving groove releases the pawl from the initial position to a position engaged with the drive portion of the drum housing upon clutch engagement.
5. An automatic inside three speed drum according to claim 3, wherein the drive portion of the drum housing comprises a ratchet ring and a fixed gear ring meshed with the outer teeth of the ratchet ring, the fixed gear ring being fixedly connected or integrally provided with the drum, the ratchet teeth of the ratchet ring meshing with the pawls when engaged and disengaged.
6. An automatic inner three-speed drum according to any one of claims 1-5, wherein the direct drive portion is provided with a pawl directly engaged with the drive portion of the drum shell.
7. A variable speed hub centrifugal clutch assembly, comprising:
the power input part is used for installing the centrifugal block, the clutch plate and the pawl;
the ratchet ring is used for outputting power to the hub shell when being meshed with the pawl;
when the clutch is combined, the centrifugal block drives the clutch plate to radially rotate to release the pawl to be meshed with the ratchet ring;
when the clutch is separated, the separation part of the ratchet ring rotates to force the pawl to be forcedly separated from the ratchet ring and is locked by the clutch plate;
wherein the clutch plate comprises a pawl receiving slot in which the pawl is partially received and locked;
the clutch plate rotates to a disengaging position where the pawl can be disengaged from the accommodating groove during gear up, and the pawl pops up from an initial position under the action of a spring and is meshed with the driving part of the hub shell; in the engagement position, the part of the pawl which is not accommodated by the pawl accommodating groove is engaged with the driving part of the hub shell when the pawl is combined in a clutch mode;
and when the gear is shifted down, the pawl enters the accommodating groove on the clutch plate again, the accommodating groove returns to the initial position, and the pawl is locked again.
8. An automatic inner three-speed hub, comprising:
a hub shaft for supporting and mounting;
a hub shell as a power output;
a first planetary gear set and a second planetary gear set mounted on the hub axle; the first planetary gear set and the second planetary gear set are arranged in a mirror image mode, and a first planet carrier of the first planetary gear set drives a second planet carrier of the second planetary gear set;
the gear ring of the first planetary gear set is provided with a first centrifugal clutch which is combined above a first pedal frequency, and the second planetary gear set is provided with a second centrifugal clutch which is combined above a second pedal frequency;
the first centrifugal clutch and the second centrifugal clutch comprise centrifugal blocks, clutch plates and pawls, the centrifugal blocks drive the clutch plates to radially rotate when the clutch plates are combined, and the clutch plates rotate to release the pawls to be meshed with a driving part of the hub shell;
wherein the clutch plate comprises a pawl receiving slot in which the pawl is partially received and locked;
the clutch plate rotates to a disengaging position where the pawl can be disengaged from the accommodating groove during gear up, and the pawl pops up from an initial position under the action of a spring and is meshed with the driving part of the hub shell; in the engagement position, the part of the pawl which is not accommodated by the pawl accommodating groove is engaged with the driving part of the hub shell when the pawl is combined in a clutch mode;
and when the gear is shifted down, the pawl enters the accommodating groove on the clutch plate again, the accommodating groove returns to the initial position, and the pawl is locked again.
9. The automatic inner three speed hub according to claim 8, wherein power is transmitted through a sleeve connection provided on the hub axle.
10. The automatic inner three speed hub according to claim 8, wherein said second planetary gear set has pawls on a carrier for directly driving the hub shell.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201811063893.9A CN108974242B (en) | 2018-09-12 | 2018-09-12 | Variable speed hub centrifugal clutch assembly and automatic internal three-speed hub |
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| CN201811063893.9A CN108974242B (en) | 2018-09-12 | 2018-09-12 | Variable speed hub centrifugal clutch assembly and automatic internal three-speed hub |
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| CN108974242A CN108974242A (en) | 2018-12-11 |
| CN108974242B true CN108974242B (en) | 2024-02-13 |
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| CN110712473B (en) * | 2019-11-25 | 2024-08-23 | 郭耀晖 | Energy return and self-speed change hub |
| CN110843421B (en) * | 2019-11-30 | 2024-09-10 | 江苏凯普斯工业科技有限公司 | Wheel axle and wheel assembly |
| CN112455157A (en) * | 2021-01-11 | 2021-03-09 | 昆山唐泽新能源科技有限公司 | Internal speed-changing hub |
| CN113859419B (en) * | 2021-10-29 | 2025-06-13 | 八方新能源(苏州)有限公司 | A three-speed mid-mounted motor capable of automatic gear shifting |
| CN114537579B (en) * | 2022-04-12 | 2025-07-15 | 广东洛梵狄智能科技有限公司 | Automatic internal transmission and bicycle |
| CN115978105A (en) * | 2022-12-07 | 2023-04-18 | 昆山知虎工业技术有限公司 | A two-speed one-way clutch automatic shift structure, transmission and control method thereof |
| CN116495093B (en) * | 2023-06-29 | 2023-09-15 | 昆山唐泽新能源科技有限公司 | Variable speed hub |
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Address after: 215300 No.36 chenjiabang Road, Kunshan Development Zone, Suzhou City, Jiangsu Province Patentee after: Jiangsu Kaipu Industrial Technology Co.,Ltd. Country or region after: China Address before: 215300 No.36 chenjiabang Road, Kunshan Development Zone, Suzhou City, Jiangsu Province Patentee before: KUNSHAN KARASAWA CLEAN ENERGY TECHNOLOGY Co.,Ltd. Country or region before: China |